solucionario beer, johnton - octava edicion parcial ultimo
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COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 1.
The masses are 1350 kg and 5400 kg.A B C
m m m= = =
Let , , and be the sought after final velocities, positive to the left.A B Cv v v
Initial velocities: ( ) ( ) ( )0 0 0
0, 8 km/h 2.2222 m/sA B Cv v v= = = =
. Truck strikes car . Plastic impact: 0First collision C B e =
( )0
Let be the common velocity of and after impact.BCv B C
:Conservation of momentum for B and C
( ) ( ) ( )0 0B C BC B B C C
m m v m v m v+ = +
( )( )6750 0 5400 2.2222BCv = + 1.77778 m/s
BCv =
Car-truck strikes carSecond collision. BC A.
Elastic impact. 1e =
( ) ( )0 0
1.77778 m/sA BC A BCv v e v v − = − − = − (1)
Conservation of momentum for A, B, and C.
( )( ) ( ) ( )( )0 0A A B C BC A A B C BC
m v m m v m v m m v+ + = + +
( )( )1350 6750 0 6750 1.77778A BCv v+ = + (2)
Solving (1) and (2) simultaneously for and ,A BCv v
2.9630 m/s, 1.18519 m/sA BC B Cv v v v= = = =
10.67 km/hA
=v
4.27 km/hB
=v
4.27 km/hC
=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 2.
Conservation of linear momentum for block, cart, and bullet together.
components : ( )0B A B C fm v m m m v= + +
( )( )
00.028 550
1.7058 m/s5 0.028 4
Bf
A B C
m v
v
m m m
= = =+ + + +
(a) 1.706 m/sfv =
Consider block and bullet alone.
Principle of impulse and momentum.
components ( ) ( ): N t mg t N mg∆ − ∆ =
components : ( ) ( )0B k A Bm v N t m m v'µ− ∆ = +
Just after impact, t∆ is negligible. The velocity then is
( )( )0
0
0.028 5503.0628 m/s
5 0.028
B
A B
'm v
v
m m
= = =+ +
Also, just after impact, the velocity of the cart is zero.
Accelerations after impact.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Block and bullet: :F ma=∑
( ) ( )k A B A B ABm m g m m aµ + = +
( )( )0.50 9.81AB k
a gµ= =
2
4.905 m/s=
Cart:
:CF ma=∑
( ) :k A B C Cm m g m aµ + =
( ) ( )( )( )0.50 5.028 9.81
4
k A B
C
C
m m ga
m
µ += =
2
6.1656 m/s=
Acceleration of block relative to cart.
( ) 2
/4.905 6.1656 11.0706 m/s
AB Ca = − − =
Motion of the block relative to the cart.
( ) ( ) ( )( )
2 2
/
/ /2
2 2
AB C
AB C AB C
v v'a s− =
In the final position, /
0AB Cv =
( ) ( )
( )( )2 2
/
/C
3.06280.424 m
2 2 11.0706AB C
AB
v's
a= − = − = −
The block moves 0.424 to the left relative to the cart.
(b) This places the block 1.000 0.424 0.576 m− = from the left end of the cart.
0.576 m from left end of cart
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 3.
( )( )22 20004000 3700The masses are 124.2 slugs, 114.9 slugs, and 1366.5 slugs
32.2 32.2 32.2A B F
m m m= = = = = =
Let , , and be the sought after velocities in ft/s, positive to the right.A B Fv v v
Initial values: ( ) ( ) ( )0 0 0
0.A B Fv v v= = =
Initial momentum of system: ( ) ( ) ( )0 0 0
0.A A B B F F
m v m v m v+ + =
There are no horizontal external forces acting during the time period under consideration. Momentum is
conserved.
0A A B B F F
m v m v m v= + +
124.2 114.9 1366.5 0A B Fv v v+ + = (1)
The relative velocities are given as
/
/
7 ft/s
3.5 ft/s
A F A F
B F B F
v v v
v v v
= − = −
= − = −
(2)
(3)
Solving (1), (2), and (3) simultaneously,
6.208 ft/s, 2.708 ft/s, 0.7919 ft/s= − = − =A B Fv v v
0.792 ft/sF
=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 4.
The masses are , , and .A B F
A B F
W W Wm m m
g g g= = =
Let the final velocities be , , and 0.34 ft/s, positive to the right.=A B Fv v v
Initial values: ( ) ( ) ( )0 0 0
0A B Fv v v= = =
Initial momentum of system: ( ) ( ) ( )0 0 0
0A A B B F F
m v m v m v+ + =
There are no horizontal external forces acting during the time period under consideration. Momentum is
conserved.
0A B F
A A B B F F A B F
W W Wm v m v m v v v v
g g g= + + = + +
Solving for ,F
W A A B B
F
F
W v W vW
v
+= − (1)
From the given relative velocities,
/
/
1.02 7.65 6.63 ft/s
1.02 7.5 6.48 ft/s
A F A F
B F B F
v v v
v v v
= + = − = −
= + = − = −
Substituting these values in (1),
( )( ) ( )( )4000 6.63 3700 6.48
49506 lb1.02
FW
− + −= − =
24.8 tonsF
W =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 5.
( ) ( )( )
3 3
3
The masses are the engine 80 10 kg , the load 30 10 kg , and the flat car
20 10 kg .
A B
C
m m
m
= × = ×
= ×
Initial velocities: ( ) ( ) ( )0 0 0
6.5 km/h 1.80556 m/s, 0.A B Cv v v= = = =
No horizontal external forces act on the system during the impact and while the load is sliding relative to the flat
car. Momentum is conserved.
Initial momentum: ( ) ( ) ( ) ( )0 0
0 0A A B C A A
m v m m m v+ + = (1)
(a) Let v′ be the common velocity of the engine and flat car immediately after impact. Assume that the
impact takes place before the load has time to acquire velocity.
Momentum immediately after impact:
( ) ( )0A B C A C
m v m m v m m v′ ′ ′+ + = + (2)
Equating (1) and (2) and solving for ,v′
( ) ( )( )
( )3
0
3
80 10 1.80556
1.44444 m/s
100 10
A A
A C
m v
v
m m
×′ = = =
+ ×
5.20 km/h′ =v
(b) Let fv be the common velocity of all three masses after the load has slid to a stop relative to the car.
Corresponding momentum:
( )A f B f C f A B C fm v m v m v m m m v+ + = + + (3)
Equating (1) and (3) and solving for ,fv
( ) ( )( )( )
3
0
3
80 10 1.80556
1.11111m/s
130 10
A Af
A B C
m v
v
m m m
×= = =
+ + ×
4.00 km/hf =v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 6.
The masses are m for the bullet and A
m and B
m for the blocks.
(a) The bullet passes through block A and embeds in block B. Momentum is conserved.
( ) ( )0 0Initial momentum: 0 0
A Bmv m m mv+ + =
Final momentum:B A A B B
mv m v m v+ +
0Equating,
B A A B Bmv mv m v m v= + +
( )( ) ( )( ) 3
0
3 3 2.5 543.434 10 kg
500 5
A A B B
B
m v m v
m
v v
−++= = = ×− −
43.4 gm =
(b) The bullet passes through block A. Momentum is conserved.
( )0 0Initial momentum: 0
Amv m mv+ =
1Final momentum:
A Amv m v+
0 1Equating,
A Amv mv m v= +
( )( ) ( )( )3
0
1 3
43.434 10 500 3 3
292.79 m/s43.434 10
A Amv m v
v
m
−
−
× −−= = =×
1293m/s=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 7.
(a) Woman dives first.
Conservation of momentum:
( )1 1
120 300 18016 0v v
g g
+− − =
( )( )
1
120 163.20 ft/s
600v = =
Man dives next. Conservation of momentum:
( )1 2 2
300 180 300 18016v v v
g g g
+− = − + −
( )( )1
2
480 180 169.20 ft/s
480
v
v
+= =
29.20 ft/s=v
(b) Man dives first.
Conservation of momentum:
( )1 1
180 300 12016 v v
g g
+′ ′− −
( )( )
1
180 164.80 ft/s
600v′ = =
Woman dives next. Conservation of momentum:
( )1 2 2
300 120 300 12016v v v
g g g
+ ′ ′ ′− = − + −
( )( )1
2
420 120 169.37 ft/s
420
v
v
′ +′ = =
29.37 ft/s′ =v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 8.
(a) Woman dives first.
Conservation of momentum:
( )1 1
120 300 18016 0v v
g g
+− − + =
( )( )
1
120 163.20 ft/s
600v = =
Man dives next. Conservation of momentum:
( )1 2 2
300 180 300 18016v v v
g g g
+ = − + −
( )( )1
2
480 180 162.80 ft/s
480
− += =
v
v 2
2.80 ft/s=v
(b) Man dives first.
Conservation of momentum:
( )1 1
180 300 12016 0v v
g g
+′ ′− − =
( )( )
1
180 164.80 ft/s
600v′ = =
Woman dives next. Conservation of momentum:
( )1 2 2
300 120 300 12016v v v
g g g
+ ′ ′ ′− = + −
( )( )1
2
420 120 160.229 ft/s
420
v
v
′− +′ = = −
2
0.229 ft/s′ =v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 9.
The masses are 9 kg.A B C
m m m= = =
Position vectors (m): 0.9 , 0.6 0.6 0.9 , 0.3 1.2A B C
= = + + = +r k r i j k r i j
2In units of kg m /s,⋅ ( ) ( ) ( )O A A A B B B C C Cm m m= × + × + ×H r v r v r v
( ) ( ) ( )( ) ( ) ( )( ) ( ) ( )
0 0 0.9 0.6 0.6 0.9 0.3 1.2 0
0 9 0 9 0 0 0 0 9
8.1 8.1 5.4 10.8 2.7
8.1 10.8 8.1 2.7 5.4
A B C
A B B C C
A C B C B
v v v
v v v v v
v v v v v
= + +
= − + − + −
= − + + − + −
i j k i j k i j k
i j k i j
i j k
But, O
H is given as ( )21.8 kg m /s− ⋅ k
Equating the two expressions for O
H and resolving into components,
: 8.1 10.8 0
: 8.1 2.7 0
: 5.4 1.8
A C
B C
B
v v
v v
v
− + =− =
− = −
i
j
k
(1)
(2)
(3)
( ) Solving for , , and ,A B C
a v v v 1.333 m/sAv = ( )1.333 m/s
A=v j
0.333m/sBv = ( )0.333m/s
B=v i
1.000 m/sCv = ( )1.000 m/s
C=v k
Coordinates of mass center G in m.
( )( ) ( )( ) ( )( )9 0.9 9 0.6 0.6 0.9 9 0.3 1.2
27
0.3 0.6 0.6
A A B B C C
A B C
m m m
m m m
+ +=+ +
+ + + + +=
= + +
r r rr
k i j k i j
i j k
Position vectors relative to the mass center in m.
( ) ( )( ) ( )( ) ( )
0.9 0.3 0.6 0.6 0.3 0.6 0.3
0.6 0.6 0.9 0.3 0.6 0.6 0.3 0.3
0.3 1.2 0.3 0.6 0.6 0.6 0.6
A A
B B
C C
′ = − = − + + = − − +
′ = − = + + − + + = +
′ = − = + − + + = −
r r r k i j k i j k
r r r i j k i j k i k
r r r i j i j k j k
( )( ) ( )( )( ) ( )( )( ) ( )
9 1.333 12 kg m/s
9 0.333 3 kg m/s
9 1 9 kg m/s
A A
B B
C C
m
m
m
= = ⋅
= = ⋅
= = ⋅
v j j
v i i
v k k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
( ) ( ) ( )
( ) ( ) ( ) ( ) ( ) ( )( ) ( ) ( )
( )
0.3 0.6 0.3 12 0.3 0.3 3 0.6 0.6 9
3.6 3.6 0.9 5.4 1.8 0.9 3.6
G A A A B B B C C Cb m m m′ ′ ′= × + × + ×
= − − + × + + × + − ×
= − − + + = + −
H r v r v r v
i j k j i k i j k k
i k j i i j k
( ) ( ) ( )2 2 21.800 kg m /s 0.900 kg m /s 3.60 kg m /sG
= ⋅ + ⋅ − ⋅H i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 10.
The masses are 9 kg.A B C
m m m= = =
Position vectors (m): 0.9 , 0.6 0.6 0.9 , 0.3 1.2A B C
= = + + = +r k r i j k r i j
Coordinates of mass center G expressed in m.
( )( ) ( )( ) ( )( )9 0.9 9 0.6 0.6 0.9 9 0.3 1.2
27
0.3 0.6 0.6
A A B B C C
A B C
m m m
m m m
+ +=+ +
+ + + + +=
= + +
r r rr
k i j k i j
i j k
Position vectors relative to the mass center expressed in m.
( ) ( )( ) ( )( ) ( )
0.9 0.3 0.6 0.6 0.3 0.6 0.3
0.6 0.6 0.9 0.3 0.6 0.6 0.3 0.3
0.3 1.2 0.3 0.6 0.6 0.6 0.6
A A
B B
C C
′ = − = − + + = − − +
′ = − = + + − + + = +
′ = − = + − + + = −
r r r k i j k i j k
r r r i j k i j k i k
r r r i j i j k j k
Angular momenta.
( ) ( ) ( )( ) ( ) ( )
O A A A B B B C C C
G A A A B B B C C C
m m m
m m m
= × + × + ×
′ ′ ′= × + × + ×
H r v r v r v
H r v r v r v
Subtracting,
( ) ( ) ( ) ( )O G A A A A B B B B C C C Cm m m′ ′ ′− = − × + − × + − ×H H r r v r r v r r v
( ) ( ) ( )( )
0A A B B C C
A A B B C C
m m m
m m m
= × + × + ×
= × + + = ×
r v r v r v
r v v v r L
is parallel to .L r 2λ λ= ⋅ = ⋅L r L L r r
( )( )
2
2 2
2
4550 , 50 N s/m
0.9λ λ⋅= = = = ± ⋅
⋅L L
r r
( )( ) ( )( ) ( )( ) ( )9 9 9 50 0.3 0.6 0.6
A A B B C C
A B C
m m m
v v v
v v v r
j i k i j k
λ+ + =
+ + = ± + +
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
( ) Resolve into components and solve for , , and .A B C
a v v v
3.333 m/sAv = ( )3.33 m/s
A=v j
1.6667 m/sBv = ( )1.667 m/s
B=v i
3.333 m/sCv = ( )3.33 m/s
C=v k
(b) Angular momentum about O expressed in 2kg m /s.⋅
( ) ( ) ( )
( ) ( ) ( )( ) ( ) ( )( ) ( ) ( )
0 0 0.9 0.6 0.6 0.9 0.3 1.2 0
0 9 0 9 0 0 0 0 9
8.1 8.1 5.4 10.8 2.7
8.1 10.8 8.1 2.7 5.4
9 4.5 9
O A A A B B B C C C
A B C
A B B C C
A C B C B
m m m
v v v
v v v v v
v v v v v
= × + × + ×
= + +
= − + − + −
= − + + − + −
= + −
H r v r v r v
i j k i j k i j k
i j k i j
i j k
i j k
( ) ( ) ( )2 2 29.00 kg m /s 4.50 kg m /s 9.00 kg m /sO
= ⋅ + ⋅ − ⋅H i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 11.
Position vectors expressed in ft.
3 6 , 6 3 , 3 3A B C
= + = + = +r i j r j k r i k
Momentum of each particle expressed in lb s.⋅
( ) ( )4 142 63 168 252
A AW
g g g= + = +v
i j i j
( ) ( )4 142 63 168 252
B BW
g g g= − + = − +v
i j i j
( ) ( )28 19 6 252 168
C CW
g g g= − = − −v
j k j k−−−−
Angular momentum of the system about O expressed in ft lb s.⋅ ⋅
( ) ( ) ( )
( )
13 6 0 0 6 3 3 0 3
168 252 0 168 252 0 0 252 168
1252 756 504 1008 756 504 756
10 0 0
A A B B C C
O A B C
W W W
g g g
g
g
g
= × + × + ×
= + + − − −
= − + − − + + + −
= + +
v v vH r r r
i j k i j k i j k
k i j k i j k
i j k
zeroO
=H
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 12.
(a) 4 4 28 36 lbA B C
W W W W= + + = + + =
( )( ) ( )( ) ( )( ) 14 3 6 4 6 3 28 3 3
36
A A B B C C A A B B C Cm m m W W m
m W
+ + + += =
= + + + + +
r r r r r rr
i j j k i k
2.667 1.333 2.667= + +i j k
( ) ( ) ( )2.67 ft 1.333 ft 2.67 ft= + +r i j k (b) Linear momentum
( )1
A A B B C C A A B B C Cm m m m W W W
g= + + = + +v v v v v v v
( )( ) ( )( ) ( )( )14 42 63 4 42 63 28 9 6
g = + + − + + − − i j i j j k
( )1252 168
32.2= −j k
( ) ( )7.83 lb s 5.22 lb sm = ⋅ − ⋅v j k (c) Position vectors relative to the mass center G (ft).
( ) ( )
( ) ( )
( ) ( )
3 6 2.667 1.333 2.667
0.333 4.667 2.667
6 3 2.667 1.333 2.667
2.667 4.667 0.333
3 3 2.667 1.333 2.667
0.333 1.333 0.333
A A
B B
C C
′ = − = + − + +
= + −′ = − = + − + +
= − + +′ = − = + − + +
= − +
r r r i j i j k
i j k
r r r j k i j k
i j k
r r r i k i j k
i j k
Angular momentum about the mass center.
( )( ) ( )( ) ( )( ) ( )( ) ( )( ) ( )( )
10.333 4.667 2.667 2.667 4.667 0.333 0.333 1.333 0.333
4 42 4 63 0 4 42 4 63 0 0 28 9 28 6
A A B B C C
G A B C
W W W
g g g
g
′ ′ ′= × + × + ×
= − + − + − − − −
v v vH r r r
i j k i j k i j k
( ) ( ) ( )
( )
1672 448 700 84 56 112 308 56 84
1896 448 672 27.827 13.913 20.870
32.2
g= − − + − − + + + −
= − − = − −
i j k i j k i j k
i j k i j k
( ) ( ) ( )27.8 ft lb s 13.91 ft lb s 20.9 ft lb sG
= ⋅ ⋅ − ⋅ ⋅ − ⋅ ⋅H i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
From Problem 14.28, O Gm= × +H r v H
2.667 1.333 2.667
0 7.83 5.22
27.826 13.913 20.870 27.827 13.913 20.870
0 0 0
O=
−
= − + + + − −= + +
i j k
H
i j k i j k
i j k
From Prob 14.11,
( ) ( ) ( )
( ) ( ) ( )
( ) ( ) ( )
( )
1
13 6 0 0 6 3 3 0 3
168 252 0 168 252 0 0 252 168
252 756 504 1008 756 504 756
10 0 0
O A A A B B B C C C
A A A B B B C C C
m m m
W W Wg
g
g
g
= × + × + ×
= × + × + ×
= + + − − −
1= − + − − + + + −
= + +
H r v r v r v
r v r v r v
i j k i j k i j k
k i j k i j k
i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 13.
Linear momentum of each particle expressed in kg m/s.⋅
3 2 4
8 6
6 15 9
A A
B B
C C
m
m
m
= − += += + −
v i j k
v i j
v i j k
Position vectors, (meters): 3 , 3 2.5 , 4 2A B C
= + = + = + +r j k r i k r i j k
( )2Angular momentum about , kg m /s .O ⋅
( ) ( ) ( )
( ) ( ) ( )
0 3 1 3 0 2.5 4 2 1
3 2 4 8 6 0 6 15 9
14 3 9 15 20 18 33 42 48
34 65 57
O A A A B B B C C Cm m m= × + × + ×
= + +− −
= + − + − + + + − + +
= − + +
H r v r v r v
i j k i j k i j k
i j k i j k i j k
i j k
( ) ( ) ( )2 2 234 kg m /s 65 kg m /s 57 kg m /sO
= − ⋅ + ⋅ + ⋅H i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 14.
Position vectors, (meters): 3 , 3 2.5 , 4 2A B C
= + = + = + +r j k r i k r i j k
( ) Mass center:a ( )A B C A A B B C Cm m m m m m+ + = + +r r r r
( )( ) ( )( ) ( )( )6 1 3 2 3 2.5 3 4 2
3 1.5 1.5
= + + + + + +
= + +
r j k i k i j k
r i j k
( ) ( ) ( )3.00 m 1.500 m 1.500 m= + +r i j k
Linear momentum of each particle, ( )kg m/s .⋅
3 2 4
8 6
6 15 9
A A
B B
C C
m
m
m
= − += += + −
v i j k
v i j
v i j k
(b) Linear momentum of the system, ( )kg m/s.⋅
17 19 5A A B B C C
m m m m= + + = + −v v v v i j k
( ) ( ) ( )17.00 kg m/s 19.00 kg m/s 5.00 kg m/sm = ⋅ + ⋅ − ⋅v i j k
Position vectors relative to the mass center, (meters).
3 1.5 0.5
1.5
0.5 0.5
A A
B B
C C
′ = − = − + −′ = − = − +′ = − = + −
r r r i j k
r r r j k
r r r i j k
(c) Angular momentum about G, ( )2kg m /s .⋅
( ) ( ) ( )
3 1.5 0.5 0 1.5 1 1 0.5 0.5
3 2 4 8 6 0 6 15 9
5 10.5 1.5 6 8 12 3 6 12
2 24.5 25.5
G A A A B B B C C Cm m m′ ′ ′= × + × + ×
= − − + − + −− −
= + + + − + + + + +
= + +
H r v r v r v
i j k i j k i j k
i j k i j k i j k
i j k
( ) ( ) ( )2 2 22.00 kg m /s 24.5 kg m /s 25.5 kg m /sG
= ⋅ + ⋅ + ⋅H i j k
( ) ( ) ( )2 2 2
3 1.5 1.5
17 19 5
36 kg m /s 40.5 kg m /s 31.5 kg m /s
m× =−
= − ⋅ + ⋅ + ⋅
i j k
r v
i j k
( ) ( ) ( )2 2 234 kg m /s + 65 kg m /s 57 kg m /sG
m+ × = − ⋅ ⋅ + ⋅H r v i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Angular momentum about O.
( ) ( ) ( )
( ) ( ) ( )( ) ( ) ( )2 2 2
0 3 1 3 0 2.5 4 2 1
3 2 4 8 6 0 6 15 9
14 3 9 15 20 18 33 42 48
34 kg m /s + 65 kg m /s 57 kg m /s
O A A A B B B C C Cm m m= × + × + ×
= + +− −
= + − + − + + + − + +
= − ⋅ ⋅ + ⋅
H r v r v r v
i j k i j k i j k
i j k i j k i j k
i j k
Note that
O Gm= + ×H H r v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 15.
The mass center moves as if the projectile had not exploded.
( ) ( )( ) ( )( )
( ) ( )
22
0
1 160 2 9.81 2
2 2
120 m 19.62 m
t gt = − = −
= −
r v j i j
i j
( )A B A A B Bm m m m+ = +r r r
( )
( )( ) ( )
1
120 120 19.62 8 120 10 20
12
120 26.033 13.333
B A B A A
B
m m m
m
= + −
= − − − −
= − +
r r r
i j i j k
i j k
( ) ( ) ( )120.0 m 26.0 m 13.33 mB
= − +r i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 16.
There are no external forces. The mass center moves as if the explosion had not occurred.
( )( ) ( )0
450 4 1800 mt= = =r v i i
( )A B C A A B B C Cm m m m m m+ + = + +r r r r
( )
( )( ) ( )( )
( )( )
1
1500 1800 300 1200 350 600
50
150 2500 450 900
3300 750 900
C A B C A A B B
C
m m m m m
m
= + + − −
= − − −
− + +
= + +
r r r r
i i j k
i j k
i j k
( ) ( ) ( )3300 m 750 m 900 mC
= + +r i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 17.
Mass center at time of first collision.
( ) ( ) ( ) ( )( ) ( ) ( ) ( )
( )( ) ( )( ) ( )( )( ) ( )
1 1 1 1
1 1 1 1
1
1
9600 2800 27.8 3600 38.4 3200 120
40 ft 22.508 ft
A B C A A B B C C
A B C A A B B C C
m m m m m m
W W W W W W
+ + = + +
+ + = + +
= − + − +
= −
r r r r
r r r r
r j j i
r i j
Mass center at time of photo.
( ) ( ) ( ) ( )( ) ( ) ( ) ( )
( )( ) ( )( )( )( )( ) ( )
2 2 2 2
2 2 2 2
2
2
9600 2800 30.3 50.7 3600 30.3 61.2
3200 59.4 45.6
40 ft 22.5375 ft
A B C A A B B C C
A B C A A B B C C
m m m m m m
W W W W W W
+ + = + +
+ + = + +
= − + + − +
+ − −
= − +
r r r r
r r r r
r i j i j
i j
r i j
Since no external horizontal forces act, momentum is conserved, and the mass center moves at constant
velocity.
( ) ( ) ( ) ( )1 1 1A B C A A B B C C
m m m m m m+ + = + +v v v v (1)
2 1t− =r r v (2)
Combining (1) and (2), ( )( ) ( ) ( ) ( )2 1 1 1 1A B C A A B B C Cm m m m m m t + + − = + + r r v v v
( )( ) ( ) ( ) ( )2 1 1 1 1A B C A A B B C CW W W W W W t + + − = + + r r v v v
( )( ) ( )( ) ( )( )1
9600 80 45.0455 0 3600 3200 66Bv t − + = + + − i j j i
Components. : 768000 211200t− = −i 3.64 st =
: 432440 3600Bv t=j
( )
( )( )432440
30.0343600 3.6363
Bv = = 30.0 ft/s
Bv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 18.
Mass center at time of first collision.
( ) ( ) ( ) ( )( ) ( ) ( ) ( )
( )( ) ( )( ) ( )( )( ) ( )
1 1 1 1
1 1 1 1
1
1
9600 2800 27.8 3600 38.4 3200 120
40 ft 22.508 ft
A B C A A B B C C
A B C A A B B C C
m m m m m m
W W W W W W
+ + = + +
+ + = + +
= − + − +
= −
r r r r
r r r r
r j j i
r i j
Mass center at time of photo.
( ) ( ) ( ) ( )( ) ( ) ( ) ( )
( )( ) ( )( )( )( )( ) ( )
2 2 2 2
2 2 2 2
2
2
9600 2800 30.3 50.7 3600 30.3 61.2
3200 59.4 45.6
40 ft 22.5375 ft
A B C A A B B C C
A B C A A B B C C
m m m m m m
W W W W W W
+ + = + +
+ + = + +
= − + + − +
+ − −
= − +
r r r r
r r r r
r i j i j
i j
r i j
Since no external horizontal forces act, momentum is conserved, and the mass center moves at constant
velocity.
( ) ( ) ( ) ( )1 1 1A B C A A B B C C
m m m m m m+ + = + +v v v v (1)
2 1t− =r r v (2)
Combining (1) and (2), ( )( ) ( ) ( ) ( )2 1 1 1 1A B C A A B B C Cm m m m m m t + + − = + + r r v v v
( )( ) ( ) ( ) ( )2 1 1 1 1A B C A A B B C CW W W W W W t + + − = + + r r v v v
( )( ) ( )( ) ( )( ) ( )1 1
9600 80 45.0455 0 3600 3200 3.4B Cv v − + = + + i j j i
Components.
( ) ( )1 1
: 432440 12240 , 35.33 ft/s,B Bv v= =j
24.1mi/hBv =
( ) ( )1 1
: 768000 10880 , 70.588 ft/s,C Cv v− = − =i
48.1mi/hCv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 19.
Projectile motion 2
0, 9.81 m/s , 0x y z
a a g a= = − = − =
( ) ( ) ( )00 0
165 m/s, 0, 0x y zv v v= = =
After the chain breaks the mass center continues the original projectile motion.
At 1.5 s,t =
( ) ( )( )0 00 165 1.5 247.5 m
xx x v t= + = + =
( ) ( )( )22
00
1 115 0 9.81 1.5 3.9638 m
2 2y
y y v t gt= + − = + − =
( )0 00
zz z v t= + =
Position of first cannon ball at this time is
1 1 1240 m, 0, 7 mx y z= = =
Definition of mass center: ( )1 2 1 1 2 2m m m m+ = +r r r
( )1 2
2 1
2 2
m m m
m m
1+= −r r r
( ) ( )
( ) ( )
30 15247.5 3.9638 240 7
15 15
255 m . m 7
= + − +
= + 7 9276 −
i j i k
i j k
Position of second cannon ball: 2 2 2
255 m, 7.93 m, 7 mx y z= = = −
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 20.
Place the vertical y axis along the initial vertical path of the rocket. Let the x axis be directed to the right (east).
Motion of the mass center: 0, 0, 0x x
a v x= = =
2
9.81 m/sy
a g= − = −
028 9.81
y yv v a t t= + = −
2 2
0 0
160 28 4.905
2
At 5.85 s, 0, 55.939 m
yy y v t a t t t
t x y
= + + = + −
= = =
:A A B B
Definition of mass center m m m= +r r r
component: 3 1 2
0 74.4 2 37.2 m
A B
B B
x x x x
x x
= += − + =
( )( ) component: 3 1 2
3 55.939 0 2 83.9 m
A B
B B
y y y y
y y
= +
= + =
.Position of part B 37.2 m(east), 83.9 m(up)
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 21.
Velocities of pieces C and D after impact and fracture.
( ) ( )
( ) ( )
2.13 m/s, 3tan30 m/s
0.7
2.12.333 m/s, 2.3333tan m/s
0.9
CC Cx y
C
DD Dx y
D
xv v
t
xv v
t
θ
′ ′= = = = °
′ ′= = = = −
Assume that during the impact the impulse between spheres A and B is directed along the x axis. Then, the y
component of momentum of sphere A is conserved.
( )0 A ym v′=
Conservation of momentum of system:
( ) ( ) ( )0: 0
A B A A C C D D xxm v m m v m v m v′ ′ ′+ = + +
( ) ( ) ( )4.8 0 3 2.33332 2
A
m m
m mv′+ = + +
( )a 2.13 m/sA′ =v
( ) ( ) ( ) ( ) ( ): 0 0A B A A C C D Dy yym m m v m v m v′ ′ ′+ = + +
( ) ( )0 0 0 3tan30 2.3333tan2 2
m m θ+ = + ° −
( )b 3
tan tan30 0.74232.3333
θ = ° = 36.6θ = °
( ) ( ) ( ) ( )22 2 23 3tan30C C Cx y
v v v= + = + o
3.46 m/sCv =
( ) ( ) ( ) ( )22 2 22.3333 2.3333tan36.6D D Dx y
v v v= + = + o
2.91m/sDv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 22.
( )( )( )( )
0 0Velocity vectors: cos30 sin 30
sin 7.4 cos7.4
sin 49.3 cos 49.3
cos 45 sin 45
A A
B B
C C
v
v
v
v
= ° + °
= ° + °
= ° − °
= ° + °
v i j
v i j
v i j
v i j
Conservation of momentum:
0A A A B B C Cm m m m= + +v v v v
Divide by and substitute data.A B C
m m m= =
( ) ( ) ( )( )
4 cos30 sin30 sin 7.4 cos7.4 sin 49.3 cos49.3
2.1 cos45 sin 45
A Bv v° + ° = ° + ° + ° − °
+ ° + °
i j i j i j
i j
Resolve into components and rearrange.
( ) ( )( ) ( )
: sin 7.4 sin 49.3 4cos30 2.1cos 45
: cos7.4 cos 49.3 4sin 30 2.1sin 45
A B
A B
v v
v v
° + ° = − °
° − ° = − °
i
j
o
o
Solving simultaneously,
(a) 2.01m/sAv =
(b) 2.27 m/sBv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 23.
( ) ( )
0190 mi/h east 278.67 ft/s
Place orgin at point of impact.
A= =v i
0 0 00, 0, 0x y z= = =
After impact the motion is projectile motion.
2
0 0
1
2t gt= + −r r v j
0
0
1
2gt
t
−= +r rv j
where ( ) ( ) ( )1600 ft 2400 ft 400 ft= − +r i j k
0
0=r
( )( )
( ) ( ) ( )
0
1600 2400 400 132.2 12
12 12 12 2
133.333 ft/s ft/s 33.333 ft/s
= − + +
= − 6.80 +
v i j k j
i j k
Impact: Conservation of momentum.
( ) ( ) ( ) 00 0A A B B A Bm m m m+ = +v v v
( ) ( )00 0
A B A
B A
B B
m m m
m m
+= −v v v
( ) ( )
( ) ( ) ( )
23000 10000133.333 6.80 33.333 278.67
13000 13000
21.537 ft/s 12.031 ft/s 58.975 ft/s
= − + −
= − +
i j k i
i j k
Components: ( )21.537 ft/s 14.69 mi/h east =i
( )58.974 ft/s 40.2 mi/h south =k
( )12.031 ft/s 8.20 mi/h down − =j
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 24.
Weight of arrow: 2 oz 0.125 lb.
Weight of bird: 6 lb.
A
B
W
W
= =
=
Conservation of momentum: Let v be velocity immediately after impact.
A B A B
A B
W W W W
g g g
++ =v v v
( )( ) ( )( )0.125 180 240 6 30
6.125
29.388 3.6735 4.8980
A A B B
A B A B
W W
W W W W
+ += + =
+ += + +
j k iv vv
i j k
( ) 2
00
1Vertical motion:
2y
y y v t gt= + −
( ) 2 210 45 3.6735 32.2 or 0.22817 2.7950 0
2t t t t= + − − − =
Solving for , 1.7898 st t =
Horizontal motion: ,x z
x v t z v t= =
( )( )( )( )29.388 1.7898 52.6 ft
4.8980 1.7898 8.77 ft
x
z
= =
= =
( ) ( )52.6 ft 8.77 ftP
= +r i k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 25.
( )( )( )
1 2 1 2
1 2 1 2
1 2 1 2
Position vectors (mm): 80 80 40 120
33 70 10 78.032
48 15 50.289
A A A A
B B B B
C C C C
= + + =
= − + − =
= − =
i j k
i j k
j k
1 2
1 2
1 2
Unit vectors: Along , 0.66667 0.66667 0.33333
Along , 0.42290 0.89707 0.12815
Along , 0.95448 0.29828
A
B
C
A A
B B
C C
= + += − + −= −
i j k
i j k
j k
λλλλλλλλλλλλ
Velocity vectors after the collisions:
A A A B B B C C Cv v v= = =v v vλλλλ λλλλ λλλλ
Conservation of momentum:
0 0 04 4 4 4
A B Cm m m m m m+ + = + +u v v v v v
Divide by m and substitute data.
( )600 750 800 2400 2400 4 4A A B B C Cv v v− + − + + = + +i j k j j λλλλ λλλλ λλλλ
Resolving into components,
: 600 0.66667 1.69160
: 5550 0.66667 3.58828 3.81792
: 800 0.33333 0.51260 1.19312
A B
A B C
A B C
v v
v v v
v v v
− = −= + +
− = − −
i
j
k
Solving the three equations simultaneously,
919.26 m/s, 716.98 m/s, 619.30 m/sA B Cv v v= = =
919 m/sAv =
717 m/sBv =
619 m/sCv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 26.
(ft):Position vectors 18D
=r k
/ /
/ /
/ /
7.5 7.5 18 19.5
18 9 18 9 18 27
13.5 13.5 18 22.5
A A D A D
B B D B D
C C D C D
r
r
r
= − = − − =
= + = + − =
= − = − − =
r i r i k
r i j r i j k
r j r j k
( )
( )
( )
/
/
/
1 : Along , 7.5 18
19.5
1Along , 18 9 18
27
1Along , 13.5 18
22.5
A D A
B D B
C D C
Unit vectors = − −
= + −
= − −
r i k
r i j k
r j k
λλλλ
λλλλ
λλλλ
Assume that elevation changes due to gravity may be neglected. Then, the velocity vectors after the
explosition have the directions of the unit vectors.
A A A B B B C C Cv v v= = =v v vλλλλ λλλλ λλλλ
0Conservation of momentum:
A A B B C Cm m m m= + +v v v v
( ) ( ) ( ) ( )18 8 6 460 45 1800 7.5 18 18 9 18 13.5 18
19.5 27 22.5
A B Cv v v
g g g g
− − = − − + + − + − −
i j k i k i j k j k
Multiply by g and resolve into components.
1080 60 10819.5 27
810 54 5227 22.5
32400 144 108 7219.5 27 22.5
A B
B C
A B C
v v
v v
v v v
= − +
− = −
− = − − −
Solving, 119.94419.5
Av = 2340 ft/s
Av =
76.63527
Bv = 2070 ft/s
Bv =
95.16022.5
Cv = 2140 ft/s
Cv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 27.
(ft):Position vectors 18D
=r k
/ /
/ /
/ /
7.5 7.5 18 19.5
18 9 18 9 18 27
13.5 13.5 18 22.5
A A D A D
B B D B D
C C D C D
r
r
r
= − = − − =
= + = + − =
= − = − − =
r i r i k
r i j r i j k
r j r j k
( )
( )
( )
/
/
/
1 : Along , 7.5 18
19.5
1Along , 18 9 18
27
1Along , 13.5 18
22.5
A D A
B D B
C D C
Unit vectors = − −
= + −
= − −
r i k
r i j k
r j k
λλλλ
λλλλ
λλλλ
Assume that elevation changes due to gravity may be neglected. Then, the velocity vectors after the explosition
have the directions of the unit vectors.
A A A B B B C C Cv v v= = =v v vλλλλ λλλλ λλλλ
/19.5
where 1950 ft/s0.010
A D
A
A
rv
t
= = =
/
271500 ft/s
0.018
B D
B
B
rv
t
= = =
C/
22.51875 ft/s
0.012
D
C
C
rv
t
= = =
( ) ( )so that 750 ft/s 1800 ft/sA
= − −v i k
( ) ( ) ( )1000 ft/s + 500 ft/s 1000 ft/sB
= −v i j k
( ) ( )1125 ft 1500 ft/sC
= − −v j k
Conservation of momentum: 0 A A B B C C
m m m m= + +v v v v
( ) ( ) ( )0750 1800 1000 500 1000 1125 1500
A B CW W W W
vg g g g
− = − − + + − + − −
k i k i j k j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Divide by g and resolve into components.
0
: 0 750 1000
: 0 500 1125
: 1800 1000 1500
A B
B C
A B C
W W
W W
Wv W W W
= − += −
− = − − −
i
j
k
(1)
(2)
(3)
Since mass is conserved, 6 lbA B C
W W W W= + + = (4)
Solving equations (1), (2), and (4) simultaneously,
(a) 2.88 lb, 2.16 lb, 0.96 lbA B C
W W W= = =
substituting into (3),
( )( ) ( )( ) ( )( )06 1800 2.88 1000 2.16 1500 0.96v− = − − −
(b) 0
1464 ft/sv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 28.
( )
( )
( ) ( )
1
1
1 1
From Eq. (14.7),n
O i i i
i
n
i i i
i
n n
i i i i i
i i
G
m
m
m v r m
m
=
=
= =
= ×
′ = + ×
′= × + ×
= × +
∑
∑
∑ ∑
H r v
r r v
r v
r v H
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 29.
( )
( )
( )
( )
( )( )
1
1
1 1
1
1
if, and only if, 0
i A i
n
A i i i
i
n
i i A i
i
n n
i i A i i i
i i
n
i i A A
i
n
i i A A A
i
A A A
A A A A
m
m
m m
m
m
m
m
=
=
= =
=
=
′= +
′= ×
′ ′= × +
′ ′= × + ×
′ ′= × +
′= − × +
′= − × +
′= − × =
∑
∑
∑ ∑
∑
∑
v v v
H r v
r v v
r v r v
r v H
r r v H
r r v H
H H r r v
This condition is satisfied if,
( ) 0 Point has zero velocity.
or ( ) Point coincides with the mass center.
or ( ) is parallel to . Velocity is directed along line .
A
A
A A A
a A
b A
c AG
==
−
v
r r
v r r v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 30.
From equation (1), ( )1
n
A i i i
i
m
=′ ′ ′= ×∑H r v
( ) ( )1
n
A i A i i A
i
m
=′ = − × − ∑H r r v v
Differentiate with respect to time.
( ) ( ) ( ) ( )1 1
n n
A i A i i A i A i i A
i i
m m
= =′ = − × − + − × − ∑ ∑H r r v v r r v v& & & & &
But , , , andi i i i A A A A
= = = =r v v a r v v a& && &
( ) ( )
( ) ( )
( ) ( )
( )
1
1
1 1
Hence, 0n
A i A i i A
i
n
i A i i A
i
n n
i A i i i A A
i i
A A A
m
m
m
m r
=
=
= =
′ = + − × −
= − × −
= − × − − ×
= − − ×
∑
∑
∑ ∑
H r r a a
r r F a
r r F r r a
M r a
&
( )if, and only if, 0A A A A
M m′ = − × =H r r a&
This condition is satisfied if
( ) 0 The frame is newtonian.
or ( ) Point coincides with the mass center.
or ( ) is parallel to . Acceleration is directed along line .
A
A
A A A
a
b A
c AG
==
−
a
r r
a r r a
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 31.
The masses are m for the bullet and A
m and B
m for the blocks.
The bullet passes through block A and embeds in block B. Momentum is conserved.
( ) ( )0 0Initial momentum: 0 0
A Bmv m m mv+ + =
Final momentum:B A A B B
mv m v m v+ +
0Equating,
B A A B Bmv mv m v m v= + +
( )( ) ( )( ) 3
0
3 3 2.5 543.434 10 kg
500 5
A A B B
B
m v m v
m
v v
−++= = = ×− −
The bullet passes through block A. Momentum is conserved.
( )0 0Initial momentum: 0
Amv m mv+ =
1Final momentum:
A Amv m v+
0 1Equating,
A Amv mv m v= +
( )( ) ( )( )3
0
1 3
43.434 10 500 3 3
292.79 m/s43.434 10
A Amv m v
v
m
−
−
× −−= = =×
(a) Bullet passes through block A. Kinetic energies.
( )( )22 3
0 0
1 1Before: 43.434 10 500 5429 J
2 2T mv
−= = × =
( )( ) ( )( )2 22 2 3
1 1
1 1 1 1After: 43.434 10 292.79 3 3 1875 J
2 2 2 2A A
T mv m v−= + = × + =
0 1Lost: 5429 1875 3554 JT T− = − = energy lost 3550 J=
(b) Bullet becomes embedded in block B. Kinetic energies.
( )( )22 3
2 1
1 1Before: 43.434 10 292.79 1861.7 J
2 2T mv
−= = × =
( ) ( )( )22
3
1 1After: 2.54343 5 31.8 J
2 2B B
T m m v= + = =
2 3Lost: 1862 31.8 1830 JT T− = − = energy lost 1830 J=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 32.
Data and results from Prob. 14.1.
Masses: 1350 kg,A B
m m= = 5400 kgc
m =
Initial velocities: 0 0
( ) ( ) 0,A Bv v= =
0( ) 8 km/h = 2.2222 m/s
cv =
Velocities after first collision:
1
( ) 0,Av =
1 1( ) ( ) 1.77778 m/s
B cv v= =
Velocities after second collision
2.9630 m/s,Av = 1.18519 m/s
B cv v= =
Initial kinetic energy: 2 2 2
0 0 0 0
1 1 1( ) ( ) ( )
2 2 2A A B B c B
T m v m v m v= + +
2 3
0
10 0 (5400)(2.2222) 13.3333 10 J
2T = + + = ×
Kinetic energy after the first collision:
( )22 2
1 1 11
1 1 1( ) ( )
2 2 2A A B B c c
T m v m v m v= + +
2 2 31 10 (1350) (1.77778) (5400)(1.77778) 10.6667 10 J
2 2= + + = ×
Kinetic energy after the second collision:
2 2 2
2
1 1 1
2 2 2A A B B c c
T m v m v m v= + +
2 2 2 31 1 1(1350)(2.9630) (1350)(1.18519) (5400)(1.18519) 10.6668 10 J
2 2 2= + + = ×
Kinetic energy lost in first collision: 3
0 12.6667 10 JT T− = ×
2.67 kJ
Kinetic energies before and after second collision:
2 110.67 kJT T= =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 33.
( )( )22 20004000 3700The masses are 124.2 slugs, 114.9 slugs, and 1366.5 slugs
32.2 32.2 32.2A B F
m m m= = = = = =
Let , , and be the sought after velocities in ft/s, positive to the right.A B Fv v v
Initial values: ( ) ( ) ( )0 0 0
0.A B Fv v v= = =
Initial momentum of system: ( ) ( ) ( )0 0 0
0.A A B B F F
m v m v m v+ + =
There are no horizontal external forces acting during the time period under consideration. Momentum is
conserved.
0A A B B F F
m v m v m v= + +
124.2 114.9 1366.5 0A B Fv v v+ + = (1)
The relative velocities are given as
/
/
7 ft/s
3.5 ft/s
A F A F
B F B F
v v v
v v v
= − = −
= − = −
(2)
(3)
Solving (1), (2), and (3) simultaneously,
6.208 ft/s, 2.708 ft/s, 0.7919 ft/sA B Fv v v= − = − =
( ) ( ) ( )22 2
1 0 0 0
1 1 1Initial kinetic energy: 0
2 2 2A A B B C
T m v m v v= + + =
2 2 2
2
1 1 1Final kinetic energy:
2 2 2A A B B C C
T m v m v m v= + +
( )( ) ( )( ) ( )( )2 2 2
2
1 1 1124.2 6.208 114.9 2.708 1366.5 0.7919
2 2 2
3243 ft lb
T = + +
= ⋅
Work done by engines: 1 1T U+
2 2T=
1U
2 2 13243 ft lbT T= − = ⋅ 1
U2
3240 ft lb= ⋅
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 34.
From the solution to Prob. 14.27,
Initial velocity of 6-lb shell: 0
1464 ft/sv =
Weights of fragments: 2.88 lb,A
W = 2.16 lb,B
W = 0.96 lbc
W =
Speeds of fragments: 1950 ft/s,Av = 1500 ft/s,
Bv = 1875 ft/s
cv =
Total kinetic energy before the explosion.
( )22 3
0 0
1 1 61464 199.69 10 ft lb
2 2 32.2
WT v
g
= = = × ⋅
Total kinetic energy after the explosion.
2 2 2
1
1 1 1
2 2 2
A B c
A B c
W W WT v v v
g g g= + +
( ) ( ) ( )2 2 21 2.88 1 2.16 1 0.961950 1500 1875
2 32.2 2 32.2 2 32.2
= + +
3297.92 10 ft lb= × ⋅
Increase in kinetic energy. 3
1 098.2 10 ft lbT T− = × ⋅
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 35.
Velocity of mass center: ( )A B A A B Bm m m m+ = +v v v
A A B B
A B
m m
m m
+=+
v v
v
Velocities relative to the mass center:
( )
( )
B A BA A B B
A A A
A B A B
A A BA A B B
B B B
A B A B
mm m
m m m m
mm m
m m m m
−+′ = − = − =+ +
−+′ = − = − =+ +
v vv v
v v v v
v vv v
v v v v
Energies:
( ) ( )( )
( ) ( )( )
2
2
2
2
1
2 2
1
2 2
A B A B A B
A A A A
A B
A B A B A B
B B B B
A B
m mE m
m m
m mE m
m m
− ⋅ −′ ′= ⋅ =
+
− ⋅ −′ ′= ⋅ =
+
v v v v
v v
v v v v
v v
( ) :a Ratio / /A B B A
E E m m=
( ) 135 km/h 37.5 m/sA
b = =v , 90 km/h 25 m/sB
= =v
62.5 m/sA B
− =v v
( )( ) ( )
( )( )
2 2
3
2
2400 1350 62.5607.5 10 J
2 3750A
E = = × 608 kJA
E =
( ) ( )( )
( )( )
2 2
6
2
2400 1350 62.51.08 10 J
2 3750B
E = = × 1080 kJB
E =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 36.
( ) :A B A A B B
Velocity of mass center m m m m+ = +v v v
A A B B
A B
m m
m m
+=+
v v
v
Velocities relative to the mass center:
( )
( )
B A BA A B B
A A A
A B A B
A A BA A B B
B B B
A B A B
mm m
m m m m
mm m
m m m m
−+′ = − = − =+ +
−+′ = − = − =+ +
v vv v
v v v v
v vv v
v v v v
Energies:
( ) ( )( )
( ) ( )( )
2
2
2
2
1
2 2
1
2 2
A B A B A B
A A A A
A B
A B A B A B
B B B B
A B
m mE m
m m
m mE m
m m
− ⋅ −′ ′= ⋅ =
+
− ⋅ −′ ′= ⋅ =
+
v v v v
v v
v v v v
v v
( ) ( )2 2
0 00 0
1 1Energies from tests: ,
2 2A A B B
E m v E m v= =
( )( ) ( )
( )
( )( ) ( )
( )
2
2 2
0 0
2
2 2
0 0
Serverities:B A B A BA
A
A A B
A A B A BB
B
B A B
mES
E m m v
mES
E m m v
− ⋅ −= =
+
− ⋅ −= =
+
v v v v
v v v v
:Ratio
2
2
A B
B A
S m
S m=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 37.
(a) A strikes B and C simultaneously.
During the impact, the contact impulses make 30° angles with the velocity 0
v
( )( )
Thus, cos30 sin30
cos30 sin30
B B
C C
v
v
= ° + °
= ° − °
v i j
v i j
By symmetry,A A
v=v i
0Conservation of momentum:
A B Cm m m m= + +v v v v
0
component: 0 0 sin 30 sin 30
component: cos30 cos30
B C C B
A B C
y mv mv v v
x mv mv mv mv
= + ° − ° == + ° + °
( )0 0
0
2,
cos30 3 3
A A
B C A B C
v v v v
v v v v v v
− −+ = = − = =o
Conservation of energy: 2 2 2 2
0
1 1 1 1
2 2 2 2A B C
mv mv mv mv= + +
( )
( )( ) ( )
( )
22 2
0 0
22 2
0 0 0 0
0 0 0 0
0 0
2
3
2
3
2 1 5 1
3 3 3 5
6 2 3
55 3
A A
A A A A
A A A A
B C
v v v v
v v v v v v v v
v v v v v v v v
v v v v
= + −
− = − + = −
+ = − = − = −
= = =
00.200
Av=v
00.693
Bv=v 30°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
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(b) A strikes B before it strikes C.
First impact; A strikes B.
During the impact, the contact impulse makes a 30° angle with the velocity 0.v
( )Thus, cos30 sin30B B
v= ° + °v i j
0Conservation of momentum.
A Bm m m= +v v v
( ) ( )( ) ( )0 0
component: 0 sin30 sin30
component: cos30 cos30
A B A By y
A B A Bx x
y m v mv v v
x v m v mv v v v
′ ′= + ° = − °
′ ′= + ° = − °
Conservation of energy:
( ) ( )
( ) ( )
( )
2 22 2
0
2 2 2
0
2 2 2 2 2 2
0 0
1 1 1 1
2 2 2 2
1 1 1cos30 sin30
2 2 2
12 cos30 cos 30 sin 30
2
A A Bx y
B B B
B B B B
mv m v m v mv
m v v v v
m v v v v v v
′ ′= + +
= − ° + ° +
= − ° + ° + ° +
( )
( )
2
0 0 0 0
0 0
3 1cos30 , sin 30 ,
2 4
3cos30 sin 30
4
B A x
A y
v v v v v v
v v v
′= ° = = ° =
′ = − ° ° = −
Second impact: A strikes C.
During the impact, the contact impulse makes a 30o angle with the velocity 0.v
( )Thus, cos30 sin30C C
v= ° − °v i j
Conservation of momentum:A A C
m m m′ = +v v v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
( ) ( )
( ) ( )
( ) ( )
( ) ( )
0
0
component: cos30 ,
1cos30 cos30
4
component: sin30
3sin30 sin30
4
A A Cx x
A A C Cx x
A A Cy y
A A C Cy y
x m v m v mv
v v v v v
y m v m v mv
v v v v v
′ = + °
′= − ° = − °
′ = − °
′= + ° = − + °
Conservation of energy:
( ) ( ) ( ) ( )2 2 2 2 2
22
2 2 2
0 0 0 0
2 2 2
0 0
2 2 2 2
0 0
1 1 1 1 1
2 2 2 2 2
1 1 3 1 1 3cos30 sin30
2 16 16 2 4 4
1 1 1cos30 cos 30
2 16 2
3 3sin30 sin 30
16 2
A A A A Cx y x y
C C C
C C
C C C
m v m v m v m v mv
m v v m v v v v v
m v v v v
v v v v v
′ ′+ = + +
+ = − ° + − + ° +
= − ° + °
+ − ° + ° +
2
0
1 30 cos30 sin30 2
2 2C C
v v v
= − ° + ° +
( )
( )
0 0
0 0 0
0 0 0
1 3 3cos30 sin30
4 4 4
1 3 1cos30
4 4 8
3 3 3sin30
4 4 8
C
A x
A y
v v v
v v v v
v v v v
= ° + ° =
= − ° = −
= − + ° = −
00.250
Av=v 60°
00.866
Bv=v 30°
00.433
Cv=v 30°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 38.
(a) Velocity of B at maximum elevation. At maximum elevation ball B is at rest relative to cart A. B A
=v v
Use impulse-momentum principle.
components:x ( )00
A A A B B A B Bm v m v m v m m v+ = + = +
0A
B
A B
m v
v
m m
=+
(b) Conservation of energy:
( ) ( )
2
1 0 1
2 2
2 2 2 0
2
2
1, 0
2
1 1 1
2 2 2 2
A
A
A A B B A B B
A B
B
T m v V
m vT m v m v m m v
m m
V m gh
= =
= + = + =+
=
( )
2 2 1 1
2 2
20
0
1
2 2
A
B A
A B
T V T V
m vm gh m v
m m
+ = +
+ =+
2 2
2 0
0
1
2
A
A
B A B
m vh m v
m g m m
= − +
2
0
2
A
A B
m vh
m m g=
+
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 39.
Velocity vectors: ( )0 0cos30 sin30v= ° − °v i j
015 ft/sv =
A A
v= −v j
( )( )sin30 cos30
cos30 sin30
B B
C C
v
v
= ° − °
= ° + °
v i j
v i j
Conservation of momentum:
0 A B C
m m m m= + +v v v v
Divide by m and resolve into components.
i: 0cos30 sin 30 cos30
B Cv v v° = ° + °
j: 0sin30 cos30 sin30
A B Cv v v v− ° = − − ° + °
Solving for and ,B Cv v
( ) ( )0 0
3 1
2 2B A C Av v v v v v= − = +
Conservation of energy: 2 2 2 2
0
1 1 1 1
2 2 2 2A B C
mv mv mv mv= + +
Divide by 1
2m and substitute for and .
B Cv v
( ) ( )2 22 2
0 0 0
2 2
0 0
3 1
4 4
2
A A A
A A
v v v v v v
v v v v
= + − + +
= + −
0
17.5 ft/s
2Av v= = 7.50 ft/s
Av =
( )315 7.5 6.4952 ft/s
2Bv = − = 6.50 ft/s
Bv =
( )115 7.5 11.25 ft/s
2Cv = + = 11.25 ft/s
Cv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 40.
Velocity vectors: ( )0 0cos45 sin 45v= ° + °v i j
015 ft/sv =
A A
v=v j
( )( )sin 60 cos60
cos60 sin 60
B B
C C
v
v
= ° − °
= ° + °
v i j
v i j
Conservation of momentum:
0 A B C
m m m m= + +v v v v
Divide by m and resolve into components.
i: 0cos45 sin 60 cos60
B Cv v v° = ° + °
j: 0sin 45 cos60 sin 60
A B Cv v v v° = − ° + °
Solving for and ,B Cv v
0 00.25882 0.5 0.96593 0.86603
B A C Av v v v v v= − = −
Conservation of energy: 2 2 2 2
0
1 1 1 1
2 2 2 2A B C
mv mv mv mv= + +
Divide by m and substitute for and .B Cv v
( ) ( )2 22 2
0 0 0
2 2
0 0
0.25882 0.5 0.96593 0.86603
1.4142 2
A A A
A A
v v v v v v
v v v v
= + + + −
= + +
0
0.70711 10.607 ft/sAv v= = 10.61 ft/s
Av =
0
0.61237 9.1856 ft/sBv v= = 9.19 ft/s
Bv =
0
0.35356 5.303 ft/sCv v= = 5.30 ft/s
Cv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 41.
1sin ,
3θ =
8cos ,
3θ = 19.471θ = °
Velocity vectors 0 0
v= −v j
( )cos sinA A
v θ θ= −v i j
( )/sin cos
B A Bu θ θ= − −v i j
/B A B A
= +v v v
C C
v=v j
Conservation of momentum: 0 /
2A B C A B A C
m m m m m m m= + + = + +v v v v v v v
Divide by m and resolve into components.
i: 0 2 cos sinA Bv uθ θ= −
−j : 0
2 sin cosA B C
v v u vθ θ= + + −
Solving for and ,A Bv u ( ) ( )0 0
1 0.94281
6A C B Cv v v u v v= + = +
Conservation of energy: 2 2 2 2
0
1 1 1 1
2 2 2 2A B C
mv mv mv mv= + +
( )2 2 2 21 1 1
2 2 2A A B C
mv m v u mv= + + +
Divide by 1
2m and substitute for and .
A Bv u
( ) ( ) ( )2
2 222 2
0 0 0
12 0.94281
6C C C
v v v v v v
= + + + +
( )22 2
0 0 00.94445 0.02857
C C Cv v v v v v− = + =
00.0286
Cv=v
[0 00.17143 0.17143
A Av v v= =v ]19.471° ,
00.1714
Av=v 19.5°
[0 / 00.96975 0.96975
B B Au v v= v ]19.471°
/B A B A
= +v v v 0.985B
=v 80.1°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 42.
1 8sin , cos , 19.471
3 3θ θ θ= = = °
C strikes B.
Conservation of momentum:
0 0
or B C B C
m m m v v v′ ′= + = −v v v
Conservation of energy:
( )22 2
0
1 1 1
2 2 2B C
mv m v mv′= +
( )22 2
0 0 C Cv v v v= − +
0Cv =
0B
v v′ =
Cord becomes taut.
Velocity vectors:
A A
v=v θ
/B A B
u=v θ
Conservation of momentum: /B A A B A
m m m m′ = + +v v v v
Divide by m and resolve into components.
+ :θ sin 2B Av vθ′ =
0
1 1sin
2 6A Bv v vθ′= =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(a) 0
6A
v=v 19.5°
+ :θ cosB Bv uθ′ = 0
cos 83
B B
v
u v θ′= =
0
1 19.471
6B
v = °
v [ 00.94281v+ ]19.471°
[ 00.95743
Bv=v ]80.8°
00.957
Bv=v 80.5°
0C
=v
Initial kinetic energy: 2
1 0
1
2T mv=
Final kinetic energy: 2 2 2
2
1 1 1
2 2 2A B C
T mv mv mv= + +
( ) ( )2
22 2
0 0
1 1 1.95743 0 0.94444
2 6 2mv mv
= + + =
(b) Fraction lost: 1 2
1
1 0.944440.05555
1
T T
T
− −= =
Fraction of energy lost = 0.0556
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 43.
(a) Use part (a) of sample Problem 14.4 with A B
m m m.= =
0 0
1
2
m
v v v
m m
= =+
0
1
2A Bv v v= =
(b) Consider initial position and position when 0θ = again.
Conservation of momentum
0 A A B B
mv m v m v= +
0B Av v v+ = (1)
Conservation of energy
2 2 2
0
1 1 1
2 2 2A B
mv mv mv= + (2)
Substituting (1) into (2),
2 2 21 1 1( )
2 2 2A B A B
m v v mv mv+ = +
0A B
mv v =
Either 0Av = with
0Bv v=
or 0Bv = with
0Av v=
(c) Consider positions when max
θ θ= and min
.θ θ=
Since /
0B Av = at these states
B Av v=
Conservation of momentum
0 A B
mv mv mv= +
0
1
2B Av v v= =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Conservation of energy would show that the elevation of B is the same for max
θ θ= and min
.θ θ=
Both A and B keep moving to the right with A and B stopping intermittently.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 44.
Relative velocity and acceleration.
/B A B A= + =v v v [vA ] + [vB/A 30° ]
/B A B A= + =a a a [aA ] + [aB/A 30° ]
Draw free body diagrams and apply Newton’s second law.
Block:
:F ma∑ = 1
cos30 sin30B B A
N m g m a− °= − ° (1)
:F ma∑ = 1 /sin30 cos30
B B A B AN m a m a°= °− (2)
Wedge:
:F ma∑ = 1sin30
A AN m a°= (3)
Rearranging (1), (2), and (3) and applying numerical data,
1
(6sin30 ) (6)(9.81)cos30A
N a+ ° = ° (1)
1 /
(sin30 ) 6 (6cos30 ) 0A B A
N a a° + − ° = (2)
1
(sin30 ) 10 0A
N a° − = (3)
Solving (1), (2), and (3) simultaneously,
1
44.325N,N = 22.2163 m/s ,
Aa = 2
/6.8243 m/s
B Aa =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Sliding motion of block relative to wedge.
2
/
/ /
( )
2
B A
B A B A
v
a s=
/ / /
2 (2)(6.8243)(1.0) 3.6944 m/sB A B A B Av a s= = =
v 3.6944
0.54136 s6.8243
B/A
B/A
t
a
= = =
Motion of wedge.
(2.2163)(0.54136) 1.1998 m/sA Av a t= = =
(a) Velocity of B relative to A. /
3.69 m/sB A
=v 30°
(b) Velocity of A . 1.200 m/sA
=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 45.
There are no external forces. Momentum is conserved.
(a) Moments about D : ( )00.9 1.8 0.9
A C C A B Bm v m v m m v= + +
( ) ( )( ) ( )0
0.90.90.5 12 2.5 3.50
1.8 1.8
A BA
C B
C C
m mm
v v v
m m
+= − = − = 3.50 m/s
Cv =
Moments about C : ( )00.9 0.9 1.8
A A B B D Dm v m m v m v= + +
( ) ( )( ) ( )( )0
0.90.90.25 12 0.5 2.5 1.750m/s
1.8 1.8
A BA
D B
D D
m mm v
v v
m m
+= − = − = 1.750 m/s
Dv =
(b) Initial kinetic energy:
( )22
1 0
1 17.5 12 540 N m
2 2A
T m v= = = ⋅
Final kinetic energy:
( ) ( ) ( )
2 2 2
2
2 2 2
1 1 1( )
2 2 2
1 1 115 2.5 7.5 3.5 15 1.750 115.78 N m
2 2 2
A B B C C D DT m m v m v m v= + + +
= + + = ⋅
Energy lost: 540 115.78 424.22 N m− = ⋅
Fraction of energy lost 424.22
0.786540
= =
( )1 2
1
0.786T T
T
−=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 46.
There are no external forces. Momentum is conserved.
(a) Moments about D : 00.9 1.8 0.9
A C C B Bm v m v m v= +
( )( ) ( )( )0
0.9 0.90.5 12 0.5 3.5 4.25
1.8 1.8
A B
C B
C C
m m
v v v
m m
= − = − = 4.25 m/sCv =
Moments about C : 0
0.9 1.8 0.9A D D B B
m v m v m v= +
( )( ) ( )( )0
0.9 0.90.25 12 0.25 3.5 2.125 m/s
1.8 1.8
A B
D B
D D
m m
v v v
m m
= − = − = 2.13 m/sDv =
(b) Initial kinetic energy:
( )22
1 0
1 17.5 12 540 N m
2 2A
T m v= = = ⋅
Final kinetic energy:
( ) ( ) ( )
2 2 2
2
2 2 2
1 1 1
2 2 2
1 1 17.5 3.5 7.5 4.25 15 2.125 147.54 N m
2 2 2
B B C C D DT m v m v m v= + +
= + + = ⋅
Energy lost: 540 147.54 392.46 N m− = ⋅
Fraction of energy lost 392.46
0.727540
= =
( )1 2
1
0.727T T
T
−=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 47.
(a) Linear and angular momentum.
00
A A B Bm m mv= + = +L v v i
0mv=L i
0
2( ) ( ) 0
3 3G
l lmv= × + − ×H j i j i
0
2
3G
lmv= −H k
Motion of mass center G. Since there is no external force,
0constant
A A B Bm m mv= + = =L v v i
03m mv=v i
0
1
3v=v i
Motion about mass center.
( ) ( )G G i i i A A A B B B
m m m′ ′ ′ ′ ′ ′ ′= = Σ × = × + ×H H r v r v r v
where 2 1
3 3A B
l , l′ ′ ′ ′= = −r j r j
2 1,
3 3A B
l lθ θ′ ′ ′ ′= = −v i v i& &
Thus, 2 2 1 1 1
23 3 3 3 3
Gl ml l m lθ θ ′ ′ ′ ′= × + − × ⋅
H j i j i& &
22
3ml θ= − k&
But HG
is constant.
2 0
0
2 2
3 3
vml lmv
lθ θ− = − =k k &
0
2 2
3 3Av l vθ′ = =&
0
1 1
3 3Bv l vθ′ = =&
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(b) After 180º rotation.
0 0
1 2
3 3A A
v v′= + = −v v v i i
0
1
3A
v= −v i
0 0
1 1
3 3B B
v v′= + = +v v v i i
0
2
3B
v=v i
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 48.
Masses: 21253.882 lb s /ft, 2 , 3 .
32.2A B A C A
m m m m m= = ⋅ = =
Conservation of angular momentum about O.
240 240 2160 ( ) ( ) ( )A A A x A y A zv v v= + + = + +r i j k v i j k
600 1320 3240 500 1100 2200B B
= + + = + +r i j k v i j k
480 960 1920 400 ( ) ( )C C C y C zv v= − − + = − + +r i j k v i j k
Since the three parts pass through O, the angular momentum about O is zero. 0
0=H
00
A A A B B B C C Cm m m= × + × + × =H r v r v r v
[ 2 3 ] 0A A A B B C C
m × + × + × =r v r v r v
Dividing by mA and using determinant form,
240 240 2160 1200 2640 6480 1440 2880 5760
( ) ( ) ( ) 500 1100 2200 400 ( ) ( )A x A y A z C y C zv v v v v
+ + − −−
i j k i j k i j k
[240( ) 2160( ) ] [2160( ) 240( ) ]A z A y A x A zv v v v= − + −i j
6 6[240( ) 240( ) ] 1.320 10 0.6 10A y A xv v+ − − × + ×k i j
0 [ 2880( ) 5760( ) ]C z C yv v+ + − −k i
6 6[1440( ) 2.304 10 ] [ 1440( ) 1.152 10 ] 0C z C yv v+ − × + − − × =j k
Dividing by 240 and equating to zero the coefficients of i, j, and k,
: ( ) 9( ) 5500 12( ) 24( ) 0A z A y C z C yv v v vi − − − − = (1)
: 9( ) ( ) 7100 6( ) 0A x A z C zv v vj − − + = (2)
: ( ) ( ) 6( ) 4800 0A y A x C yv v vk − − − = (3)
Conservation of linear momentum.
0( )
A A B C C C A B Cm m m m m m+ + = + +v v v v
0( 2 3 ) 6 ( )
A A C C Am m+ + =v v v v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Dividing by mA and substituting given data,
( ) + ( ) ( ) (2)(500 1100 2200 ) (3)[ 400 + ( ) ( ) ] (6)(1500)A x A y A z C y C zv v v + v + v+ + + + − =i j k i j k i j k k
Separating into components,
: ( ) 1000 1200 0A xvi + − = (4)
: ( ) 2200 3( ) 0A y C yv vj + + = (5)
: ( ) 4400 3( ) 9000A z C zv vk + + = (6)
From (4), ( ) 200 ft/sA xv =
Solving (3) and (5) simultaneously,
( ) 200 ft/s ( ) 800 ft/sA y C yv v= = −
Solving (2) and (6) simultaneously,
( ) 1300 ft/s ( ) 1100 ft/sA z C zv v= =
(200 ft/s) (200 ft/s) (1300 ft/s)A
= + +v i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 49.
Let the system consist of spheres A and B.
State 1. Instant cord DC breaks.
( ) 01
3 1
2 2A
m mv
= − −
v i j
( ) 01
3 1
2 2B
m mv
= −
v i j
( ) ( )1 01 1A Bm m mv= + = −L v v j
1
0
1
2 2v
m
= = −Lv j
Mass center lies at point G as shown.
( ) ( ) ( )1 11
0
3 3
2 2
3
2
G A Bl m l m
lmv
= × + − ×
=
H j v j v
k
2 2 2
1 0 0 0
1 1
2 2T mv mv mv= + =
State 2. The cord is taut. Conservation of linear momentum:
(a) 0
1
2D
v= = −v v j
00.500
Dv v=
Let ( )2
and A A B B
= + = +v v u v v u
2 12
A Bm m m= + + =L v u u L
B A B Au u= − =u u
( )2
2G A B A
lmu lmu lmu= + =H k k k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(b) Conservation of angular momentum:
( ) ( )2 1G G
=H H
0
32
2A
lmu lmv=k k
0
3
4A B
u u v= =
00.750u v=
( ) 2 2 2
2
2 2
0 0
1 1 12
2 2 2
1 1 9 9 13
2 2 16 16 16
A BT m v mu mu
mv mv
= + +
= + + =
(c) Fraction of energy lost: 13
1 2 16
1
1 3
1 16
T T
T
−− = =
1 2
1
0.1875T T
T
− =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 50.
The system is spheres A and B and the ring D.
Initial velocities: ( )0cos30 sin30
Av= − ° − °v i j
( )0cos30 sin30
0
B
D
v= − ° − °
=
v i j
v
Locate the mass center.
( ) ( )0
0
4
sin30 cos30 sin30 cos30
1
4
A Bm m m
ml ml
l
= +
= − ° + ° + − ° − °
= −
r r r
i j i j
r i
Velocity of mass center.
( ) ( )0 0
0
4
cos30 sin30 cos30 sin30
1
4
A Bm m m
mv mv
v
= +
= − ° − ° + ° − °
= −
v v v
i j i j
v j
(a) Motion of mass center 0
t= +r r v
0
1 1
4 4l v t= − −r i j
(b) / /G AG A B G B
m m= × + ×H r v r v
( )
( )
0
0
1cos30 cos30 sin 30
4
1 cos30 cos30 sin 30
4
l l mv
l l mv
= − + ° × − ° − °
+ − − ° × ° − °
i j i j
i j i j
0
7
4G
lmv=H k
(c) 2 2 2
0
1 1
2 2A B
T mv mv mv= + =
2
0T mv=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 51.
Let m be the mass of one ball.
Conservation of linear momentum: 0
( ) ( )m mΣ = Σv v
0 0 0( ) ( ) ( )
A B C A B Cm m m m m m+ + = + +v v v v v v
Dividing by m and applying numerical data,
(0.5 ft/s) [(3.75 ft/s) ( ) ] [( ) ( ) ] (6.5 ft/s) 0 0B y C x C yv v v+ + + + = + +i i j i j i
Components:
: 0.5 3.75 ( ) 6.5C x
x v+ = + ( ) 2.25 ft/sC xv =
: ( ) ( ) 0B y C yy v v+ = (1)
Conservation of angular momentum about O:
0[ ( )] [ ( )]m mΣ × = Σ ×r v r v
where rA = 0, rB = 0, (1.5 ft)(cos30 sin30 )C
= ° + °r i j
( )( )1.5 cos30 + sin 30 [ ( ) ( ) ] 0C x C ym v m vi j i j° ° × + =
Since their cross product is zero, the two vectors are parallel.
( ) ( ) tan30 2.25 tan30 1.2990 ft/sC y C xv v= ° = ° =
From (1), ( ) 1.2990 ft/sB yv = −
( ) 1.299 ft/sB yv = −
(2.25 ft/s) (1.299 ft/s)C
+=v i j
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 52.
Let m be the mass of one ball.
Conservation of linear momentum: 0
( ) ( )m mΣ = Σv v
0 0 0( ) ( ) ( )
A B C A B Cm m m m m m+ + = + +v v v v v v
Dividing by m and applying numerical data,
0 [(6 ft/s) ( ) ] [( ) ( ) ] (8 ft/s) 0 0B y C x C yv v v+ + + + = + +i j i j i
Components:
: 6 ( ) 8C x
x v+ = ( ) 2 ft/sC xv =
: ( ) ( ) 0B y C yy v v+ = (1)
Conservation of angular momentum about O:
0[ ( )] [ ( )]m mΣ × = Σ ×r v r v
where rA = 0, rB = 0, (1.5 ft)(cos45 sin 45 )C
= ° + °r i j
(1.5)(cos45 sin 45 ) [ ( ) ( ) ] 0C x C ym v m v° + ° × + =i j i j
Since their cross product is zero, the two vectors are parallel.
( ) ( ) tan 45 2 tan 45 2 ft/sC y C xv v= ° = ° =
From (1), ( ) 2 ft/sB yv = −
( ) 2.00 ft/sB yv = −
(2.00 ft/s) (2.00 ft/s)C
+=v i j
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 53.
Conservation of linear momentum: 0
A B A B
A B
W W W W
g g g g
+ = +
v v v
After multiplying by g, ( ) ( ) ( )7.2 5.76 1.44 4.8 2.4 2.4A B Bx yv v v+ = + +i j j i j
i: ( )41.472 2.4B xv= ( ) 17.28 ft/s
B xv =
j: ( )10.348 4.8 2.4A B yv v= − ( ) 4.32 2B Ay
v v= −
Speeds relative to the mass center: ( ) ( )( )1 13 8 8 ft/s
3 3A
u lω= = =
( ) ( )( )2 23 8 16 ft/s
3 3B
u lω= = =
Initial kinetic energy: ( ) ( )2 2 2 2
1 0 0
1 1 1
2 2 2
A B A BA Bx y
W W W WT v v u u
g g g g
= + + + +
( ) ( ) ( )2 22 2
1
1 7.2 1 4.8 1 2.45.76 1.44 8 16 18.2517 ft lb
2 32.2 2 32.2 2 32.2T
= + + + = ⋅
Final kinetic energy: ( ) ( )2 22
2
1 1 1
2 2 2
A B BA B Bx y
W W WT v v v
g g g= + +
( ) ( )2 22
2
1 4.8 1 2.4 1 2.417.28 4.32 2
2 32.2 2 32.2 2 32.2A A
T v v = + + −
20.2236 0.6440 11.8234
A Av v= − +
Conservation of energy: 1 2T T=
(a) 20.2236 0.6440 6.4283 0, 6.9919 ft/s
A A Av v v− − = = 6.99 ft/s
A=v
( ) ( )( ) ( ) ( )4.32 2 6.9919 9.6638 ft/s 17.28 ft/s 9.6638 ft/sB Byv = − = − = −v i j
19.80 ft/sB
=v 29.2°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Conservation of angular momentum about O:
( ) ( )( ) ( )
( ) ( ) ( )( ) ( )( )
0 0 0 01
2
3 3
7.2 4.8 2.47.44 5.76 1.0 8 2.0 16 6.0047 ft lb s
32.2 32.2 32.2
A B B B
O A B G A Bx x
W W W l W lH y m m v H y v u u
g g g g
= − + + = − + + +
= − + + = − ⋅ ⋅
( ) ( )2
( )A BO A A B B A B yy
W WH m v a m v b v a v b
g g= + = +
4.8 2.4(6.9919) ( 9.6638)(24) 1.0423 17.2868
32.2 32.2a a
= + − = −
( ) ( )2 1
1.0423 17.2868 6.0047O O
H H a= − = −
(b) 10.82 fta = 10.82 fta =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 54.
Conservation of linear momentum: 0
A B A B
A B
W W W W
g g g g
+ = +
v v v
( ) ( )0
9 6 37.68 10.8 6.72
32.2 32.2 32.2
= + −
v j i j
(a) ( ) ( )03.6 ft/s 2.88 ft/s= +v i j
04.61 ft/s=v 38.7°
Let Al be the distance from G to A and
Bl be the distance from G to B.
or 2A B A
A B B A A
B
W W Wl l l l l
g g W= = =
Let ω be the spin rate.
Initial kinetic energy: ( ) ( )2 22
1 0
1 1 1
2 2 2
A B A B
A B
W W W WT v l l
g g g gω ω
= + + +
( ) ( ) ( )
( )
2 22 2
1
2
1 9 1 6 1 33.6 2.88 2
2 32.2 2 32.2 2 32.2
2.9703 0.27950
A A
A
T l l
l
ω ω
ω
= + + +
= +
Final kinetic energy: 2 2
2
1 1
2 2
A B
A B
W WT v v
g g= +
( ) ( )2 2 2
2
1 6 1 37.68 10.8 6.72 13.0324
2 32.2 2 32.2T
= + + =
Conservation of energy: 2 1
T T= .
( ) ( )213.0324 2.9703 0.27950 6.000 ft/s
A Al lω ω= + =
Conservation of angular momentum about O:
( ) ( ) ( ) ( ) ( )
( )( ) ( ) ( )( )
( ) ( )( )
0 0 0 01
2
2
9 6 30 7.5 3.6 2 2
32.2 32.2 32.2
7.5466 0.55901 7.5466 3.3540
A B A BO A A B By x
A A A
A A
W W W WH x v y v l l l l
g g g g
l l l
l l
ω ω
ω ω
ω
= + − + +
= − + +
= − + = − +
( ) ( ) ( )( ) ( )( )
( ) ( )
2
2 1
6 37.68 5.58 6.72 21.6
32.2 32.2
5.5382 ft lb s
: 5.5382 7.5466 3.3540 0.600 ft
A BO A B y
O O A A
W WH v a v b
g g
H H l l
= + = + −
= − ⋅ ⋅
= − = − + =
(b) 2 1.200 ft B A A Bl l l l l= = = + 1.800 ftl =
(c) 6.00
10.000.600
A
A
l
l
ωω = = = 10.00 rad/sω =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 55.
Velocities in m/s. Lengths in meters. Assume masses are 1.0 for each ball.
Before impacts: ( ) ( ) ( )00 0 04 , 0
A B Cv= = = =v i i v v
After impacts: ( ) ( )1.92 , , A B B B C Cx yv v v= − = + =v j v i j v i
Conservation of linear momentum: 0 A B C
= + +v v v v
i: ( ) ( )4 0 4B C B Cx xv v v v= + + = −
j: ( ) ( )0 1.92 0 1.92B By yv v= − + + =
Conservation of energy: 2 2 2 2
0
1 1 1 1
2 2 2 2A B C
v v v v= + +
( ) ( ) ( ) ( )22 2 2 21 1 1 1 14 1.92 1.92 4
2 2 2 2 2C Cv v= + + − +
24 3.6864 0
C Cv v− + =
( ) ( )( )24 4 4 3.6864
2 0.56 2.56 or 1.442
Cv
± −= = ± =
Conservation of angular momentum about :B′
( )( )( ) ( )( )
00.75 1.8
0.75 4 1.8 1.65 1.92 2.712
2.712
A C
C
C
v a v cv
cv
c
v
= − +
= − − =
=
If 1.44,Cv = 1.8833 off the table. Rejectc =
If 2.56,Cv = 1.059c =
Then, ( ) 4 2.56 1.44, 1.44 1.92B Bxv = − = = +v i j
Summary.
(a) 2.40 m/sB
=v 53.1°
2.56 m/sC
=v
(b) 1.059 mc =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 56.
Velocities in m/s. Lengths in meters. Assume masses are 1.0 for each ball.
Before impacts: ( ) ( ) ( )00 0 05 , 0
A B Cv= = = =v i i v v
After impacts: ( ) ( ), , 3.2A A B B B Cx yv v v= − = + =v j v i j v i
Conservation of linear momentum: 0 A B C
= + +v v v v
i: ( ) ( )5 0 3.2 1.8B Bx xv v= + + =
j: ( ) ( )0 0 A B B Ay yv v v v= − + + =
Conservation of energy: 2 2 2 2
0
1 1 1 1
2 2 2 2A B C
v v v v= + +
( ) ( ) ( ) ( ) ( )2 2 2 2 21 1 1 1 15 1.8 3.2
2 2 2 2 2A Av v= + + +
(a) 25.76 2.4
A Av v= = 2.40 m/s
A=v
( ) 2.4B yv = 1.8 2.4
B= +v i j 3.00 m/s
B=v 53.1°
Conservation of angular momentum about :B′
( )00.75 1.8
A Cv a v cv= − +
0
1.8 0.75A A C
av v cv v= + −
( )( ) ( )( ) ( )( )1.8 2.4 1.22 3.2 0.75 5 4.474= + − =
(b) 4.474 4.474
2.4A
a
v
= = 1.864 ma =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 57.
Use a frame of reference that is translating with the mass center G of the system. Let
0v be its velocity.
0 0v=v i
The initial velocities in this system are ( ) ( )0 0,
A B′ ′v v and ( )
0,
C′v each having a magnitude of .lω They are
directed 120° apart. Thus,
( ) ( ) ( )0 0 0
0A B C′ ′ ′+ + =v v v
(a) Conservation of linear momentum:
( ) ( ) ( ) ( ) ( ) ( )0 0 00 0 0A B C A B Cm m m m m m′ ′ ′+ + = − + − + −v v v v v v v v v
( ) ( ) ( )0 0 00
A B Cv v v v v v= − + − − + −j i j i i i
Resolve into components.
i: ( )0 0
1 13 0 4.5
3 3C Cv v v v− = = =
01.500 m/s=v
j: 0 2.6 m/sA B B Av v v v− = = =
Conservation of angular momentum about G:
( ) ( ) ( )2
0 0 03
G A A B B C Cml m rω= = × − + × − + × −H k r v v v v r v v
( ) ( ) ( ) ( )( )( ) ( ) ( ) ( )
( )( ) ( )( )
2
0
2 2
3
10.260 2.6 0.150 4.5 0.45033 m /s
3
A B A C C A B C
A C A C
l v v v
a d v av dv
l
ω
ω
= − × + × − + +
= × + − × = +
= + =
k r r j r i r r r i
i v j j i k
Conservation of energy: ( )2 2 2 2
1
1 332 2
T ml mlω ω= =
0 0
0 0
0 0
2.6 1.5 3.00 m/s
2.6 1.5 3.00 m/s
4.5 1.5 3.00 m/s
A A
B B
C C
− = − − =
− = − − − =
− = − − =
v v j i v v
v v j i v v
v v i i v v
( ) ( ) ( )2 2 2
2 0 0 0
1 1 1
2 2 2A B C
T m m m= − + − + −v v v v v v
1 2T T=
( ) ( ) ( )2 2 22 23 1 1 13 3 3
2 2 2 2ml m m mω = + +
3 m/slω =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(b) 2 2
0.45033 m /s0.1501 m
3 m/s
ll
l
ωω
= = = 150.1 mml =
(c) 3 m/s
0.1501
l
l
ωω = = 19.99 rad/sω =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 58.
Use a frame of reference that is translating with the mass center G of the system. Let 0
v be its velocity.
0 0v=v i
The initial velocities in this system are ( ) ( )0 0, ,
A B′ ′v v and ( )
0,
C′v each having a magnitude of .lω They are
directed 120° apart. Thus,
( ) ( ) ( )0 0 0
0A B C′ ′ ′+ + =v v v
Conservation of linear momentum:
( ) ( ) ( ) ( ) ( ) ( )0 0 00 0 0A B C A B Cm m m m m m
′ ′ ′+ + = − + − + −v v v v v v v v v
( ) ( ) ( )0 0 00
A B Cv v v v v v= − + − − + −j i j i i i
Resolve into components.
i: 0
3 0Cv v− = ( )( )0
3 3 0.4 1.2 m/sCv v= = =
j: 0A Bv v− =
B Av v=
Initial kinetic energy: 2 2 2
1 0
1 13 3
2 2T mv ml ω = +
Final kinetic energy: 2 2 2 2 2
2
1 1 1 1
2 2 2 2A B C A C
T mv mv mv mv mv= + + = +
Conservation of energy: 2 1
T T= Solve for 2
Av .
( ) ( ) ( ) ( )2 2 2 22 2 2
0
3 3 1 3 3 10.4 0.75 1.2
2 2 2 2 2 2A Cv v l vω= + − = + −
(a) 2 20.36375 m /s ,= 0.6031 m/s
Av = 0.603 m/s
A=v
0.603 m/sB
=v
1.200 m/sC
=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Use a frame of reference moving with velocity 0.v
Conservation of angular momentum about G.
( ) ( ) ( )2
0 0 03
G A A B B C Cml m r m mω= = × − + × − + × −H k r v v v v r v v
( ) ( ) ( ) ( )( )2
03
A B A C C A B Cl v v vω = − × + × − + +k r r j r i r r r i
( ) ( ) ( ) ( ) ( )3A C A C
l l a d v av dvω = × + − × = +k i v j j i k
( )( )( ) ( )3 0.075 0.75 0.130 1.200Av d= +
(b) ( )( )0.1406 0.1083 0.603 0.0753 md = − = 75.3 mmd =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 59.
Mass flow rate. As the fluid moves from section 1 to section 2 in time ∆t, the mass ∆m moved is
( )m A lρ∆ = ∆
Then, 1
( )dm m A lAv
dt t t
ρ ρ∆ ∆= = =∆ ∆
Data: 3 2 6 2
11000 kg/m , 500 mm 500 10 m , 25 m/sA vρ = = = × =
6(1000)(500 10 )(25) 12.5 kg/sdm
dt
−= × =
Principle of impulse and momentum.
:
1( ) 0m v P t∆ − ∆ =
m dmP v v
t dt
∆= =∆
(12.5)(25)P =
312 NP =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 60.
Consider velocities measured with respect to the plate, which is moving
with velocity V. The velocity of the stream relative to the plate is
1u v V= − (1)
Mass flow rate. As the fluid moves from section 1 to section 2 in time ∆t,
the mass ∆m moved is
( )m A lρ∆ = ∆
Then ( )dm m A l
Audt t t
ρ ρ∆ ∆= = =∆ ∆
(2)
Principle of impulse and momentum.
( ) ( ) 0m u P t∆ − ∆ =
2m dmP u u Au
t dtρ∆= = =
∆
Pu
Aρ=
From (1), 1 1
PV v u v
Aρ= − = −
Data: 2 6 2400 N, 600 mm 600 10 mP A
−= = = ×
3
130 m/s, 1000 kg/mv ρ= =
6
40030
(1000)(600 10 )V −= −
× 4.18 m/sV =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 61.
Let F be the force that the wedge exerts on the stream. Assume that the fluid speed is constant. 60 ft/s.v =
Volumetric flow rate: 3475 gal/min ft /sQ = = 1.0583
Mass flow rate: ( )3 362.4slug/ft 1.0584 ft /s 2.051 slug/s
32.2
dmQ
dtρ = = =
Velocity vectors: ( )1, cos30 sin 30v v= = ° + °v i v i j
( )2cos45 sin 45v= ° − °v i j
Impulse – momentum principle:
( ) ( ) 1 22 2
m mm t
∆ ∆∆ + ∆ = +v F v v
( ) ( )
( )( )( )( ) ( )
1 2
1 1
2 2
1 1cos30 sin 30 cos 45 sin 45
2 2
2.051 60 ft/s 0.21343 0.10355
26.26 lb 12.74 lb
m
t
dmv
dt
∆ = + − ∆
= ° + ° + ° − ° −
= − −
= − −
F v v v
i j i j i
i j
i j
Force that the stream exerts on the wedge:
( ) ( )26.26 lb 12.74 lb− = +F i j drag 26.3 lb=
lift 12.74 lb=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 62.
For a fixed observer, the upstream velocity is ( )48 ft/s .=v i
Volumetric flow rate: 3500 gal/min ft /sQ = = 1.1141
Mass flow rate: ( )3 362.4slug/ft 1.1141 ft /s 2.1590 slug/s
32.2
dmQ
dtρ = = =
Use a frame of reference that is moving with the wedge to the left at 12 ft/s. In this frame of reference the
upstream velocity vector is
( ) ( )48 12 60 ft/s .= − − =u i i i
For the moving frame of reference the mass flow rate is ( )602.1590 2.6987 slug/s.
48
dm u dm
dt v dt
′ = = =
Velocity vectors: ( )1, cos30 sin 30u u= = ° + °u i u i j
( )2cos45 sin 45u= ° − °u i j
Let F be the force that the wedge exerts on the stream.
Impulse-momentum principle:
( ) ( ) 1 22 2
m mm t
∆ ∆∆ + ∆ = +u F u u
( ) ( )
( )( )( )( ) ( )
1 2
1 1
2 2
1 1cos30 sin30 cos45 sin 45
2 2
2.6987 60 0.21343 0.10355
34.6 lb 16.76 lb
m
t
dmu
dt
∆ = + − ∆
′ = ° + ° + ° − ° −
= − −
= − −
F u u u
i j i j i
i j
i j
Force that the stream exerts on the wedge
( ) ( )34.6 lb 16.76 lb− = +F i j drag 34.6 lb=
lift 16.76 lb=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 63.
Let F be the force exerted on the chips. Apply the impulse-momentum principle to the chips. Assume that
the feed velocity is negligible.
( ) ( ) Ct m∆ = ∆F v
( )cos25 sin 25C
m dmv
t dt
∆ = = ° + ° ∆ F v i j
( )( )1060 cos25 sin 25
32.2
= ° + °
i j
( ) ( )16.89 lb 7.87 lb= +i j
0: 0x x x
F D FΣ = − =
16.89 lbx
D =
Force on truck hitch at D:
16.89 lbx
D− = − 16.89 lbx
D− =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 64.
Initial momentum: ( ) 0.A
m∆ =v
Impulse – momentum principle.
( )( ) ( )x yF F t m+ ∆ = ∆i j v
( )o o
cos35 sin35x y
m dmF F v
t dt
∆ + = = + ∆ i j v i j
x component:
oEngine thrust cos35x
dmF v
dt= =
Data: 3 388 m /min m /s
60Q = = 31000 kg/mρ =
( ) 81000 133.333 kg/s
60
dmQ
dtρ = = =
( )( ) o
133.333 50 cos35 5461 Nx
F = =
5.46 kNx
F =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 65.
Weight: (600)(9.81) 5886 NW mg= = =
Principle of impulse and momentum.
Moments about F:
1 1 1 2
( ) (3 ) (2 ) ( ) ( ) ( ) 3( )m v a mv a m v a W t c R t L m v h∆ + ∆ + ∆ + ∆ − ∆ = ∆
1 2
16 3
m mR cW av hv
L t t
∆ ∆ = + + ∆ ∆
Data: 6 m, 4 m, 1.5 m, 0.8 m, 40 kg/sm dm
L c a ht dt
∆= = = = =∆
[ ]1(4)(5886) (6) (1.5) (3) (40) (3) (0.8) (4) (40) 4040 N
6R = + − =
4040 N=R
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 66.
Assume A B
u u u= =
Principle of impulse and momentum.
Moments about O :
( ) ( ) ( )A c B
R m u x t R m u∆ + ∆ = ∆F kk r
( ) ( ) ( ) 0c B Ax t R m u u∆ = ∆ − =r F k
The line of action of F passes through point O.
Components : ( ) ( ) ( )sin cosA B
m u F t m uα θ∆ + ∆ = ∆
sin (1 cos )m
F ut
α θ∆= −∆
(1)
Components : ( ) ( )0 cos sinF t m uα θ+ ∆ = ∆
cos sinm
F ut
α θ∆=∆
(2)
Dividing (2) by (1),
22sin
1 cos 2tan tan
sin 22sin cos
2 2
θθ θα θ θθ
−= = =
.2
θα =
Thus point C lies at the midpoint of arc AB.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 67.
( ) ( )( )80013.333 L/s 1.000 kg/L 13.333 L/s 13.333 kg/s
60
dmQ Q
dtρ= = = = =
( ) ( )( )30 m/s 30 m/s sin 40 cos 40B C
= = ° + °v j v i j
Apply the impulse – momentum principle.
x components: ( ) ( )( )0 30sin 40x
A t m+ ∆ = ∆ °
( ) ( )( )30sin 40 13.333 30sin 40x
mA
t
∆= ° = °∆
257Nx
A =
y components: ( )( ) ( ) ( )( )30 30cos40y
m A t m∆ + ∆ = ∆ °
( ) ( )30cos40 30 13.333 30cos40 30y
mA
t
∆= ° − = ° −∆
93.6 N= − 93.6 Ny
A =
moments about :A ( )( )( ) ( )0.060 30
Am M t∆ + ∆
( )( )( ) ( )( )( )0.180 30cos40 0.300 30sin 40m m= ∆ ° − ∆ °
( ) ( ) ( )1.8 1.6484A
m M t m∆ = ∆ − ∆
( ) ( )( )3.4484 13.333 3.4484 46.0 N mA
mM
t
∆= − = − = − ⋅∆
46.0 N mA
= ⋅M
274 N=A 20.0°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 68.
Mass flow rate: 3 3
2
62.4 lb/ft 40 ft /min1.29193 lb s/ft
60 s/min32.2 ft/s
dmQ
dt g
γ= = = ⋅
75 ft/sA Bv v= =
Use impulse - momentum principle.
moments about :D ( )( ) ( )( ) ( )15 23 15
sin 60 cos6012 12 12
A Am v m v C t
− ∆ ° + ∆ ° − ∆
( ) 3
12B
m v
= ∆
( )( )( )15 15 23 3sin 60 cos60 1.29193 75 0.37420
12 12 12 12A
mC v
t
∆ = − ° + ° − = − ∆
29.006 lbC = − 0, 29.0 lbx y
C C= = −
x component: ( ) ( ) ( )cos60A x B
m v D t m v∆ ° + ∆ = ∆
( ) ( )( )cos60 1.29193 75 75cos60x B A
mD v v
t
∆ = − ° = − ° ∆ 48.4 lb
xD =
y component: ( ) ( ) ( )sin 60 0A ym v C t D t∆ ° + ∆ + ∆ =
( )( )sin 60 29.006 1.29193 75 sin 60y A
mD C v
t
∆= − − ° = + − °∆
54.9 lby
D = −
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 69.
Volumetric flow rate: 3300 gal/min 0 ft /sQ = = .6684
Mass flow rate: ( )3 362.4slug/ft 0.6684 ft /s 1.2954 slug/s
32.2
dmQ
dtρ = = =
90 ft/sA Bv v= =
Use the impulse – momentum principle.
Moments about C: ( ) ( ) ( ) cosA P B
m v a W t l m v bθ∆ − ∆ = ∆
(a) ( ) ( )( ) ( )( )( )( )
90 4 /12 90 1/12cos 1.2954 0.7287
40 1
A B
p
m v a v b
t W lθ
−∆ −= = =∆
43.23θ = ° 43.2θ = °
x components: ( ) ( ) ( ) cosA x B
m v C t m v θ∆ + ∆ = ∆
( ) ( )( )cos 1.2954 90cos 90 31.63 lbx B A
mC v v
tθ θ∆= − = − = −
∆
y components: ( ) ( ) ( )0 siny p BC t W t m v θ+ ∆ − ∆ = − ∆
( ) ( )( )sin 40 1.2954 90 sin 39.84 lby p B
mC W v
tθ θ∆= − = − = −
∆
(b) [31.63 lb=C ] [39.84 lb+ ] 50.9 lb=C 51.6°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 70.
Volumetric flow rate: 3300 gal/min 0 ft /sQ = = .6684
Mass flow rate: ( )3 362.4slug/ft 0.6684 ft /s 1.2954 slug/s
32.2
dmQ
dtρ = = =
, 45A Av v v θ= = = °
Use the impulse-momentum principle.
moments about C: ( ) ( ) ( ) cosA p Bm v a W t l m v bθ∆ − ∆ = ∆
(a) ( )( ) ( )( )( )
( ) cos 40 1 cos 45
87.338 ft/s4 1/
1.295412 12
pA B
W lv v
a b m t
θ °= = = =
− ∆ ∆ −
87.3 ft/sv =
x components: ( ) ( ) ( ) cosA x B
m v C t m v θ∆ + ∆ = ∆
( ) ( )[ ]cos 1.2954 87.338cos45 87.338 33.137 lbx B A
mC v v
tθ∆= − = ° − = −
∆
y components: ( ) ( ) ( )0 siny p BC t W t m v θ+ ∆ − ∆ = − ∆
( )( )sin 40 1.2954 87.338 sin 45 40.0 lby p B
mC W v
tθ∆= − = − ° = −
∆
(b) [33.137 lb=C ] [40 lb+ ] 51.9 lb=C 50.4°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 71.
Symbols: mass flow ratedm
dt=
exhaust relative to the airplaneu =
speed of airplanev =
drag forceD =
Principle of impulse and momentum.
( ) ( ) ( )m v D t m u∆ + ∆ = ∆
m dm D
t dt u v
∆ = =∆ −
Data: 900 km/h = 250 m/sv =
600 m/su =
35 kN 35000ND = =
35000
600 250
dm
dt=
− 100 kg/sdm
dt=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 72.
Let F be the force exerted on the slipstream of one engine. Then, the force exerted on the airplane is −2F as
shown.
Statics.
0B
MΣ =
( ) ( )( )0.9 4.8 2 0W F− =
( )( )
( )( )0.9 6000
2 4.8F =
562.5 lb=
Calculation of .
dm
dt
mass density volume density area length= × = × ×
( ) ( ) ( )B B
B B B
A v tm A l A v t
g
γρ ρ ∆∆ = ∆ = ∆ =
B B
m dm A v
t dt g
γ∆ = =∆
Force exerted on the slipstream: ( )B A
dmF v v
dt= −
Assume that Av , the speed far upstream, is negligible.
( ) 2 20
4
B B
B B
A vF v D v
g g
γ γ π = − =
( )( )( )
( ) ( )2 2 2
2 2
4 562.5 32.247058.9 ft /s
6.6 0.075B
Fgv
Dπ γ π= = =
84.0 ft/s B
=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 73.
Let F be the force exerted on the slipstream of one engine.
( )B A
dmF v v
dt= −
Calculation of .
dm
dt mass density volume density area length= × = × ×
( ) ( ) ( )B B
B B B
A v tm A l A v t
g
γρ ρ ∆∆ = ∆ = ∆ =
2 or
4
B B
B
m A v dmD v
t g dt g
γ γ∆ π = = ∆
Assume that ,Av the velocity far upstream, is negligible.
( ) ( ) ( )2 22 0.0750 6.6 60 286.87 lb
4 32.2 4B B
F D v vg
γ π π = − = =
The force exerted by two slipstreams on the airplane is 2 .F− 2 573.74 lbF− =
Statics.
0:B
MΣ =
( )0.9 4.8 2 9.3 0W F A− − − =
( )( ) ( )( )10.9 6000 4.8 573.74
9.3A = −
284.5 lb= 285 lb=A
0: 2 0x x
F F B= − − =
2 573.74 lbx
B F= − =
( )0: 284.5 6000 0y y y
F A B W BΣ = + − = + − =
5715.5 lby
B =
[573.74 lb=B ] [5715.5 lb+ ] 5740 lb=B 84.3°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 74.
Use a frame of reference moving with the plane. Apply the impulse-momentum principle. Let F be the force that
the plane exerts on the air.
x components: ( ) ( ) ( )A Bm u F t m u∆ + ∆ = ∆
( ) ( )B A B A
m dmF u u u u
t dt
∆= − = −∆
(1)
moments about B: ( ) ( ) 0A B
e m u M t− ∆ + ∆ =
B A
dmM e u
dt= (2)
Let d be the distance that the line of action is below B.
B
Fd M= B A
B A
M eud
F u u= =
− (3)
Data: 90 kg/s,dm
dt= 600 m/s,
Bu = 4 me =
(a) 480 km/h 133.333 m/sA
u = =
From (1), ( )( ) 390 600 133.333 42 10 NF = − = × 42.0 kNF =
From (2), ( )( )
( )4 133.333
600 133.333d =
− 1.143 md =
(b) 960 km/h 266.67 m/sA
u = =
From (1), ( )( ) 390 600 266.67 30 10 NF = − = × 30.0 kNF =
From (2), ( )( )
( )4 266.67
600 266.67d =
− 3.20 md =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 75.
The thrust on the fluid is ( )B A
dmF v v
dt= −
Calculation of dm
dt. mass density volume density area length= × = × ×
( ) ( )B B Bm A l A v tρ ρ∆ = ∆ = ∆
B B
m dmA v
t dtρ∆ = =
∆
whereB
A is the area of the slipstream well below the helicopter and Bv is the corresponding velocity in the
slipstream. Well above the blade, 0.Av ≈
Hence, 2
BF Avρ=
( ) ( ) ( )2 23
3 2
1.21 kg/m 9 m 24 m/s4
44.338 10 kg m/s
π =
= × ⋅
44.3 kNF =
The force on the helicopter is 44.3 kN .
Weight of helicopter: 15kNH
=W
Weight of payload: P P
W=W
Statics: 0y H PF F W WΣ = − − =
44.3 15 29.3 kN.P H
W F W= − = − = 29.3 kNW =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 76.
Let dm
dt= mass flow rate, u = discharge velocity relative to the airliner, speed of airliner,v = and
thrustF = of the engines.
0F D− = ( ) 0dm
u v Ddt
− − =
Configuration before control surface malfunction:
1
720= 22.36 slug/s, 1860 ft/s, 560 mi/h 821.33 ft/s
32.2
dmu v
dt= = = =
( )( ) 1 122.36 1860 821.33 0 23225 lbD D− − = =
Drag force factor: ( )
2 2 21
1 1 1 1 2 2
1
23225 0.03443 lb s /ft
821.33
DD k v k
v= = = = ⋅
After control surface malfunction: 2 2
2 11.2 0.04131 lb s /ftk k= = ⋅
When the new cruising speed is attained,
( ) 2
2 2 20
dmu v k v
dt− − =
( )( ) 2
2 222.36 1860 0.04131 0v v− − =
Solving for v2, 2768.6 ft/sv =
2524 mi/hv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 77.
Apply the impulse - momentum principle to the moving air. Use a frame of reference that is moving with the
airplane. Let F be the force on the air.
270 km/h 75 m/s
600 m/s
v
u
= ==
( ) ( ) ( )2 sin 20
2
mm v F t u
∆− ∆ + ∆ = °
( ) ( )
( )( ) 3
sin 20 sin 20
120 75 600sin 20 33.6 10 N
m dmF v u v u
t dt
F
∆= + ° = + °∆
= + ° = ×
Force on airplane is .−F 33.6 kN=F
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 78.
Symbols: n = number engines operating
dm
dt= mass flow rate for one engine
u = discharge velocity relative to jetliner = 800 m/s
v = speed of jetliner
F = thrust force ( )dm
n u vdt
= −
D = drag force 2kv=
Force balance.
0F D− = 2( )dm
n u v kvdt
− =
2 1
( )
v dm
n u v k dt=
−
All 3 engines operating: 3, 900km/h = 250 m/sn v= =
2(250) 1
37.879 m/s3(800 250)
dm
k dt= =
−
(a) One engine lost: n = 2
2
37.8792(800 )
v
v
=−
275.758 60606 0v v+ − =
211.2m/sv = 760 km/hv =
(b) 2 engines lost: n = 1
2
37.879800
v
v
=−
237.879 30303 0v v+ − =
156.16 m/sv =
562 km/hv =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 79.
Let u be the velocity of the stream relative to the velocity of the blade. ( )u v V= −
Mass flow rate: A
mAv
tρ∆ =
∆
Principle of impulse and momentum.
( ) ( ) ( ) cost
m u F t m u θ∆ − ∆ = ∆
( )1 cos ( ) (1 cos )t A A
mF u Av v V
tθ ρ θ∆= − = − −
∆
where Ft is the tangential force on the fluid.
The force Ft on the fluid is directed to the left as shown. By Newton’s law of action and reaction, the
tangential force on the blade is Ft to the right.
Output power: out( ) (1 cos )
t A AP FV Av v V Vρ θ= = − −
(a) V for maximum power output.
out ( 2 ) (1 cos ) 0
A
dPA v V
dVρ θ= − − =
1
2Av V=
(b) Maximum power.
out max
1 1( ) (1 cos )
2 2A A A A
P Av v v vρ θ = − −
3
out max
1( ) (1 cos )
4A
P Avρ θ= −
Input power = rate of supply of kinetic energy of the stream
2 2 3
in
1 1 1 1( )
2 2 2A A A
mP m v v Av
t tρ∆ = ∆ = = ∆ ∆
COSMOS: Complete Online Solutions Manual Organization System
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© 2007 The McGraw-Hill Companies.
(c) Efficiency. out
in
p
pη =
3
( ) (1 cos )
1
2
A A
A
Av v V V
Av
ρ θηρ
− −=
2 1 (1 cos )A A
V V
v vη θ
= − −
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 80.
Data: 240
slugs/s,32.2
dm
dt= = 7.4534 2200 ft/s,u = 570 mi/h 836 ft/sv = =
( ) ( )( )7.4534 2200 836 10166 lbdm
F u vdt
= − = − =
(a) Power used to propel airplane:
( )( ) 6
110166 836 8.499 10 ft lb/sP Fv= = = × ⋅
propulsion power 15450 hp=
Power of kinetic energy of exhaust:
( ) ( )( )22
1
2P t m u v∆ = ∆ −
( ) ( )( )2 2 6
2
1 17.4534 2200 836 6.934 10 ft lb/s
2 2
dmP u v
dt= − = − = × ⋅
(b) Total power: 6
1 215.433 10 ft lb/sP P P= + = × ⋅
total power 28060 hp=
(c) Mechanical efficiency: 6
1
6
8.499 100.551
15.433 10
P
P
×= =×
mechanical efficiency 0.551=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 81.
Kinetic energy of fluid in slipstream passing in time .t∆
2 21 1 mass speed density volume speed
2 2T∆ = × = × ×
21
density area length speed2
= × × ×
( ) ( )2 21 1
2 2A l v Av t vρ ρ= ∆ = ∆
31
2
TAv
tρ∆ =
∆
Input power 31
2
dTAv
dtρ= =
Data: 31.2 kg/mρ =
( )22 26.5 33.183 m
4 4A d
π π= = =
30 km/h 8.333 m/sv = =
(a) ( )( )( )3 311.2 33.183 8.333 11.521 10 N m/s
2
dT
dt= = × ⋅
11.52 kJ/s
Input power 11.521 kWdT
dt= =
(b) Output power ( )( )0.4 11.521 4.61 kW= =
output power 4.61 kW=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 82.
Kinetic energy of fluid in slipstream passing in time .t∆
2 21 1 mass speed density volume speed
2 2T∆ = × = × ×
21
density area length speed2
= × × ×
( ) ( )2 21 1
2 2A l v Av t vρ ρ= ∆ = ∆
31
2
TAv
tρ∆ =
∆ (1)
Data: output power 3.5 kW 3500 W= =
3500input power 10000 W
0.35= =
input power 10,000 W, 36 km/h 10 m/sdT
vdt
= = = =
Using (1), ( )( )( )( )
2
3 3
2 10000216.667 m
1.2 10
dTA
dtvρ= = =
(a) ( )( )24 16.6674
4
Ad A d
ππ π
= = =
4.61 md =
(b) From above, 10.00 kJ/sdT
dt=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 83.
Mass flow rate:
mass density volume
density area length
= ×= × ×
( ) ( )m bd l bdv tρ ρ∆ = ∆ = ∆
dm m
bdvdt t
ρ∆= =∆
1 dm
Q bdvdtρ
= =
Continuity of flow: 1 2
Q Q Q= =
1 2
1 2
,
Q Qv v
bd bd=
Resultant pressure forces:
1 1 2 2 p d p dγ γ= =
2
1 1 1 1
1 1
2 2F p bd bdγ= =
2
2 2 2 2
1 1
2 2F p bd bdγ= =
Apply impulse-momentum principle to water between
sections 1 and 2.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
( ) ( ) ( ) ( )1 1 2 2m v F t F t m v∆ + ∆ − ∆ = ∆
( )1 2 2 1
mv v F F
t
∆ − = −∆ ( )2 2
2 1
1 2
1
2
Q QQ b d d
bd bdρ γ
⋅ − = −
( ) ( )( )
2
2 1
1 2 2 1
1 2
1
2
Q d db d d d d
bd d
ργ
−= + −
Noting that ,gγ ρ=
( )1 2 1 2
1
2Q b gd d d d= +
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 84.
Mass flow rate:
mass density volume
density area length
= ×= × ×
( ) ( )m bd l bdv tρ ρ∆ = ∆ = ∆
dm m
bdvdt t
ρ∆= =∆
1 dm
Q bdvdtρ
= =
Continuity of flow: 1 2
Q Q Q= =
1 2
1 2
,
Q Qv v
bd bd=
Resultant pressure forces:
1 1 2 2 p d p dγ γ= =
2
1 1 1 1
1 1
2 2F p bd bdγ= =
2
2 2 2 2
1 1
2 2F p bd bdγ= =
Apply impulse-momentum principle to water between
sections 1 and 2.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
( ) ( ) ( ) ( )1 1 2 2m v F t F t m v∆ + ∆ − ∆ = ∆
( )1 2 2 1
mv v F F
t
∆ − = −∆ ( )2 2
2 1
1 2
1
2
Q QQ b d d
bd bdρ γ
⋅ − = −
( ) ( )( )
2
2 1
1 2 2 1
1 2
1
2
Q d db d d d d
bd d
ργ
−= + −
Noting that ,gγ ρ=
( )1 2 1 2
1
2Q b gd d d d= +
Data: 1 2
9.81 m/s, 3 m, 1.25 m, 1.5 mg b d d= = = =
( )( )( )( ) 313 9.81 1.25 1.5 1.25 1.5 15.09 m /s
2Q = + =
315.09 m /sQ =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 85.
From hydrostatics, the pressure at section 1 is 1
.p rh ghρ= =
The pressure at section 2 is 2
0.p =
Calculate the mass flow rate using section 2.
mass density volume density area length= × = × ×
( ) ( )2 2A Am l v tρ ρ∆ = ∆ = ∆
2A
dm mv
dt tρ∆= =
∆
Apply the impulse-momentum principle to fluid between sections 1 and 2.
( ) ( ) ( )1 1 1m v p A t m v∆ + ∆ = ∆
1 1 1
dm dmv p A v
dt dt+ =
( ) ( )1 1 1 2 1
dmp A v v A v v v
dtρ= − = −
But 1v is negligible,
1,p ghρ= and 2v gh=
( )1 22ghA A ghρ ρ= or
1 22A A=
2 22
4 4D d
π π =
2
Dd =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 86.
The flow through each arm is 1.25 gal/min.
3
3 3gal 1 ft 1 min5 11.1408 10 ft /s
min 7.48 gal 60 sQ − = = ×
( )3
3 3
2
3
62.4 lb/ftQ 11.1408 10 ft /s
32.2 ft/s
21.590 10 lb s/ft
dmQ
dt g
γρ
−
= = = ×
= × ⋅
Consider the moment about O exerted on the fluid stream of one arm.
Apply the impulse-momentum principle. Compute moments about O.
First, consider the geometry of triangle OAB. Using first the law of
cosines,
( ) ( ) ( ) ( )2 2 2 o6 4 2 6 4 cos120OA = + −
76 in. 0.72648 ftOA = =
Law of sines. o
sin sin120
4 76
β =
o
23.413 ,β =
o o
60 36.587α β= − =
Moments about O:
( )( )( ) ( ) ( )( ) ( )( )( )0 sinO O s
m v M t OA m v OA m OAα ω∆ + ∆ = ∆ − ∆
( ) ( )
( ) ( )( ) ( )( )
2
23
sin
21.590 10 0.72648 60 sin 36.587 0.72648
0.56093 0.011395 lb ft
O s
mM OA v OA
tα ω
ω
ω
−
∆ = − ∆ = × −
= − ⋅
Moment that the stream exerts on the arm is .
OM−
Friction couple for one arm:
( )10.275 0.06875 lb ft
4F
M = = ⋅
Balance of moments on one arm:
0 F O F O
M M M M− = =
0.06875 0.56093 0.011395ω= −
43.19 rad/s 412 rpmω = =
412 rpmω =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 87.
Consider the conservation of the horizontal component of momentum of the railroad car of mass 0
m and the
sand mass .qt
( ) 0 0
0 0 0
0
m vm v m qt v v
m qt= + =
+ (1)
0 0
0
dx m vv
dt m qt= =
+
Integrating, using 0
0x = and x L= when ,L
t t=
( )0 0 0 0
0 00 0
0
0 0 0
0
ln ln
ln
L Lt t
L
L
m v m vL vdt dt m qt m
m qt q
m v m qt
q m
= = = + − ++=
∫ ∫
0
0 0 0
lnL
m qt qL
m m v
+ =
0 0/0
0
qL m vLm qte
m
+ =
(a) Final mass of railroad car and sand 0 0/
0 0
qL m vLm qt m e+ =
(b) Using (1), 0 0/0 0 0 0
0 0
qL m vL
L
m v m vv e
m qt m
−= =+
0 0/
0
qL m vLv v e
−=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 88.
Apply the impulse-momentum principle.
Moments about C : ( )( ) ( ) ( ) ( )( )0.9 3 1.8 1.65A B
m v D t W t m v− ∆ + ∆ − ∆ = − ∆
( )
( )( ) ( ) ( )( ) ( )( )
1.8 10.9 1.65
3 3
1.8 4000 1100 0.9 4.5 1.65 4.5 2287.5 N
3 3
A B
mD W v v
t
∆= + −∆
= + − =
2.29 kN=D
x components: ( ) ( ) ( )A x Bm v C t m v∆ + ∆ = ∆
( ) ( )( )100 4.5 4.5 0x B A
mC v v
t
∆= − = − = ∆
y components: ( ) ( ) ( )0 0y
C t D t W t+ ∆ + ∆ − ∆ =
4000 2287.5 1712.5 Ny
C W D= − = − =
1.712 kN=C
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 89.
Let ρ be the mass per unit length of chain. Apply the impulse - momentum to the entire chain. Assume that the
reaction from the floor it equal to the weight of chain still in contact with the floor.
Calculate the floor reaction.
( )R g l yρ= − 1y
R mgl
= −
Apply the impulse-momentum principle.
( ) ( ) ( ) ( )yv P t R t gl t y y vρ ρ ρ+ ∆ + ∆ − ∆ = + ∆
( ) ( ) ( )P t y v gl t R tρ ρ∆ = ∆ + ∆ − ∆
(a) ( )yP v gl l y g
tρ ρ ρ∆= + − −
∆ Let
y dyv
t dt
∆ = =∆
2P v gyρ ρ= + ( )2mP v gy
l= +
(b) From above, 1y
mgl
= −
R
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 90.
(a) Let ρ be the mass per unit length of chain. The force P supports the weight of chain still off the floor.
P gyρ= mgy
Pl
=
(b) Apply the impulse-momentum principle to the entire chain.
( ) ( ) ( ) ( )yv P t R t gl t g y y vρ ρ ρ− + ∆ + ∆ − ∆ = − + ∆
( ) ( ) ( ) ( )R t gl t P t g y vρ ρ∆ = ∆ − ∆ − ∆
y
R gl gy vt
ρ ρ ρ ∆= − −∆
Let 0.t∆ → Then, y dy
vt dt
∆ = = −∆
( ) 2R g l y vρ ρ= − + ( ) 2mg l y v
l = − + R
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 91.
Let ρ be the mass per unit length of chain. Consider the impulse-momentum applied to the link being brought to
rest at point C.
Calculation of .m∆
( ) ( )m l v tρ ρ∆ = ∆ = ∆
Impulse-momentum principle:
( ) 0m v C t− ∆ + ∆ =
( ) 0v t v C tρ− ∆ + ∆ =
2C vρ=
Impulse – momentum applied to the moving portion of the chain. Consider only the changes in momentum and
forces contributing to moments about O in the diagram.
Moments about O:
( ) [ ] ( )m v gh C t m vρ∆ + − ∆ = ∆
C ghρ=
Equating the two expressions for C,
2v ghρ ρ=
2vh
g=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 92.
Let ρ be the mass per unit length of chain. Assume that the weight of any chain above the hole is supported by
the floor. It and the corresponding upward reaction of the floor are not shown in the diagrams.
Case 1. Apply the impulse-momentum principle to the entire chain.
( )( )( ) ( ) ( )( )
( )( )
yv gy t y y v v
yv y v y v y v
y vy vgy v y
t t t
ρ ρ ρ
ρ ρ ρ ρ
ρ ρ ρ ρ
+ ∆ = + ∆ + ∆
= + ∆ + ∆ + ∆ ∆
∆ ∆∆ ∆= + +∆ ∆ ∆
Let 0.t∆ → ( )dy dv dgy v y yv
dt dt dtρ ρ ρ ρ= + =
Multiply both sides by .yv ( )2 dgy v yv yv
dtρ ρ=
Let dy
vdt
= on left hand side. ( )2 dy dgy yv yv
dt dtρ ρ=
Integrate with respect to time. ( ) ( )2g y dy yv d yvρ ρ=∫ ∫
( )231 1
3 2gy yvρ ρ= or 2 2
3v gy= (1)
Differentiate with respect to time. 2 2
23 3
dv dyv g gvdt dt
= =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(a)
1
3
dva g
dt= = 0.333g=a
(b) Set in (1)y l= 2 2
3v gl= 0.817 gl=v
Case 2. Apply conservation of energy using the floor as the level for from which the potential energy is
measured.
1 10, 0T V= =
2
2 2
1,
2 2
yT mv V gyρ= = −
1 1 2 2T V T V+ = +
2 21 10
2 2mv gyρ= −
2 2
2 gy gyv
m l
ρ= = (1)
Differentiating with respect to y, 2
2dv gy
vdy l
=
(a) Acceleration. dv gy
a vdy l
= = gy
l=a
(b) Setting in (1),y l= 2v gl= gl=v
Note: The impulse-momentum principle may be used to obtain the force that the edge of the hole exerts
on the chain.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 93.
750 lb/s,dW
dt=
1 75023.292 lb s/ft
32.2
dm dW
dt g dt= = = ⋅
Thrust of one engine: ( )( ) 3 12500 23.292 291.15 10 lb
dmP u
dt= = = ×
For 3 engines, 33 873.4 10 lbP = ×
Thrust 873 kips=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 94.
Thrust of one engine: 3
3 1200 10400 10 lb.
3P
×= = ×
But, dm
P udt
=
3400 10
32 lb s/ft12500
dm P
dt u
×= = = ⋅
( )( )32.2 32 1030 lb/sdW dm
gdt dt
= = = 1030 lb/sdW
dt=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 95.
Thrust, .
dmP u
dt=
F P mg maΣ = − =
P u dm
a g gm m dt
= − = −
Data: 15 kg/sdm
dt=
As rocket is fired: 1500 kgm =
0
159.81 0.01 9.81
1500
ua u= − = − (1)
As all the fuel is consumed: 1
1500 1200 300 kg.m = − =
1
159.81 0.05 9.81
300
u
a u= − = − (2)
From the given data, 2
1 0220 m/sa a− = (3)
Using (1) and (2) for 1a and
0a and substituting into (3),
0.04 220u = 5500 m/su =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 96.
Thrust: dm
P u uqdt
= =
Since u and dm
dt are constant, P is also constant.
:F maΣ =
P mg ma− =
( )P m a g= +
( )min maxm a g= +
( )( )1500 25 9.81= +
352.215 10 N= ×
(a) Fuel consumption rate.
3
52.215 10
450
Pq
u
×= =
116.0 kg/sq =
(b) Mass of fuel consumed.
( )( )fuel116.0 15.6m qt= =
fuel
1810 kgm =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 97.
Apply the principle of impulse and momentum to the satellite plus the fuel expelled in time ∆t.
: ( )( ) ( )( )mv m m v v m v v v= − ∆ + ∆ + ∆ + ∆ −
( ) ( ) ( )( ) ( ) ( )( ) ( )mv m v m v m v m v m v m v= + ∆ − ∆ − ∆ ∆ + ∆ + ∆ ∆ − ∆
( ) ( ) 0m v u m∆ − ∆ =
( )dmm t
dt∆ = − ∆
v dv u dm
t dt m dt
∆ = = −∆
1 1 1
0 00
v t m
v m
u dm dmdv dt u
m dt m= − = −∫ ∫ ∫
1 0
1 0
0 1
ln lnm m
v v u u
m m
− = − =
0 1 0
1
expm v v
m u
− =
Data: 1 0
2430 m/s,v v− = 0
4200 m/s 5000 kgu m= =
1
5000 2430exp 1.7835
4200m
= =
1
2800 kgm =
fuel 0 1
5000 2800m m m= − = − fuel
2200 kgm =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 98.
Data from Problem 14.97: 0
5000 kg, 4200 m/sm u= =
1 0 fuel
5000 1500 3500 kgm m m= − = − =
Apply the principle of impulse and momentum to the satellite plus the fuel expelled in time ∆t.
: ( )( ) ( )( )mv m m v v m v v v= − ∆ + ∆ + ∆ + ∆ −
( ) ( ) ( )( ) ( ) ( )( ) ( )mv m v m v m v m v m v m v= + ∆ − ∆ − ∆ ∆ + ∆ + ∆ ∆ − ∆
( ) ( ) 0m v u m∆ − ∆ =
( )dmm t
dt∆ = − ∆
v dv u dm
t dt m dt
∆ = = −∆
1 1 1
0 00
v t m
v m
u dm dmdv dt u
m dt m= − = −∫ ∫ ∫
1 0
1 0
0 1
ln lnm m
v v u u
m m
− = − =
1 0
50004200 ln
3500v v v∆ = − = 1498 m/sv∆ =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 99.
Apply conservation of momentum to the rocket plus the fuel.
( )( ) ( )( )( ) ( ) ( )( ) ( ) ( )( ) ( )
mv m m v v m v v v
mv m v m v m v m v m v m v
= − ∆ + ∆ + ∆ + ∆ −
= + ∆ − ∆ − ∆ ∆ + ∆ + ∆ ∆ − ∆
( ) ( ) 0m v u m∆ − ∆ =
( )dmm t
dt∆ = − ∆
v dv u dm
t dt m dt
∆ = = −∆
1 1 1
0 00
v t m
v m
u dm dmdv dt u
m dt m= − = −∫ ∫ ∫
1 0 0
1 0
0 1 1
ln ln lnm m W
v v u u um m W
− = − = =
Data: 1 0
360 ft/sv v− =
( )0 111,600 lb, 11,600 1000 10,600 lbW W= = − =
11,600
360 ln10,600
u= 3990 ft/su =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 100.
Apply conservation of momentum to the rocket plus the fuel.
( )( ) ( )( )( ) ( ) ( )( ) ( ) ( )( ) ( )
mv m m v v m v v v
mv m v m v m v m v m v m v
= − ∆ + ∆ + ∆ + ∆ −
= + ∆ − ∆ − ∆ ∆ + ∆ + ∆ ∆ − ∆
( ) ( ) 0m v u m∆ − ∆ =
( )dmm t
dt∆ = − ∆
v dv u dm
t dt m dt
∆ = = −∆
1 1 1
0 00
v t m
v m
u dm dmdv dt u
m dt m= − = −∫ ∫ ∫
1 0
1 0
0 1
ln lnm m
v v u u
m m
− = − =
0 1 0 0
1 1
expm v v W
m u W
− = =
Data: 1 0
450 ft/s,v v− = 5400 ft/su =
0 1 fuel 1
1200 lbW W W W= + = +
1
1
1200 450exp 1.08690
5400
W
W
+ = =
1
12000.08690
W=
113810 lbW =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 101.
See sample Problem 14.8 for derivation of
0 0
0 0
ln lnm m qt
v u gt u gtm qt m
−= − = − −−
(1)
Note that g is assumed to be constant.
Set dy
vdt
= in (1) and integrate with respect to time.
0
0 0 0
0
20
0
0
ln
1ln
2
h t t
t
mh dy vdt u gt dt
m qt
m qtu dt gt
m
= = = − −
−= − −
∫ ∫ ∫
∫
Let 0
0
m qtz
m
−= 0
qdz dt
m= − or 0
mdt dz
q= −
( )0 0
2 20 0
20 0 0 0 0
0 0 0 0
20 0
0 0
0 0 0
0 0
1 1ln ln
2 2
1ln 1 ln 1
2
11 ln 1 1
2
ln 1 1 ln 1
zz
z z
m u m uh z dz gt z z z gt
q q
m u m qt m qt m mgt
q m m m m
m u qt m qtgt
q m m
m u m qt m qtut
q m m
= − = + −
− −= − − − −
−= − − + −
− −= − + − −
∫
2
20 0
0
1
2
1ln
2
gt
m u m qtut ut gt
q m
−
−= + − −
20 0
0
1ln
2
m mh u t t gt
q m qt
= − − − −
(2)
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Data: 20
0
7300226.7 lb s /ft
32.2
Wm
g= = = ⋅
260
8.0745 lb s/ft32.2
wq
g= = = ⋅
&
2fuel
fuel
4000124.22 lb s /ft
32.2
Wm
g= = = ⋅
fuel124.22
15.385 s8.0745
mt
q= = =
2
0226.7 124.22 102.48 lb s /ftm qt− = − = ⋅
1500 ft/su =
( )( )2226.7 226.7 11500 15.385 15.385 ln 32.2 15.385
8.0745 102.48 2h
= − − −
4150 fth =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 102.
Thrust force dm
P u uqdt
= =
Mass of rocket plus unspent fuel 0
m m qt= −
Acceleration: 0
P uqa
m m qt= =
−
Integrating with respect to time to obtain the velocity,
0 00 0
0
t t qv v adt v u dt
m qt= + = +
−∫ ∫
( ) 0
0 0 0 0
0
ln ln lnm qt
v u m qt m v um
− = − − − = − (1)
Integrating again to obtain the displacement,
0
0 0 0
0
lnt m qt
s s v t u dtm
−= + − ∫
Let 0 0
0 0
or
m qt q mz dz dt dt dz
m m q
−= = − = −
( ) ]0 0
0 0
0 0
00 0 0 0
0 0
0 0 0 0
0 0
0 0
0
0 0 0
0 0
0 0
ln ln
ln 1 ln 1
1 ln 1 1
ln 1 1 ln 1
zz
z z
o
m u m us s v t zdz z z z
q q
mm u m qt m qt ms v t
q m m m m
m u qt m qts v t
q m m
m u m qt m qts v t ut
q m m
= + + = −
− −= + + − − −
−= + + − − +
− −= + + − + − −
∫
0 0
0 0
0
lnm u m qt
s v t ut utq m
−= + + + −
0 0
0 0
0
lnm m
s s v t u t tq m qt
= + + − − −
(2)
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Data: 0
7500 ft/s 7500 360 7860 ft/sv v= = + =
( )( )fuel fuel
100060 s 0.5176 slug/s
32.2 60
m Wt q
t gt= = = = =
0
0
11600360.25 slugs
32.2
Wm
g= = =
0
11600 1000329.19 slugs
32.2 32.2m qt− = − =
0
0s =
From (1), 329.19
7860 7500 ln360.25
u= −
360.25
360 ln329.19
u= 3993 ft/su =
From (2), ( )( ) 360.25 360.250 7500 60 3993 60 60 ln
0.5176 329.19s
= + + − −
6460.6 10 ft= × 87.2 mis =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 103.
See sample Problem 14.8 for derivation of
0 0
0 0
ln lnm m qt
v u gt u gtm qt m
−= − = − −−
(1)
Note that g is assumed to be constant.
Set dy
vdt
= in (1) and integrate with respect to time.
0
0 0 0
0
20
0
0
ln
1ln
2
h t t
t
mh dy vdt u gt dt
m qt
m qtu dt gt
m
= = = − −
−= − −
∫ ∫ ∫
∫
Let 0 0
0 0
or
m qt q mz dz dt dt dz
m m q
−= = − = −
( ) ]0 0
2 20 0
20 0 0 0 0
0 0 0 0
20 0
0 0
0 0 0
0 0
1 1ln ln
2 2
1ln 1 ln 1
2
11 ln 1 1
2
1ln 1 1 ln 1
2
zz
z z
m u m uh zdz gt z z z gt
q q
m u m qt m qt m mgt
q m m m m
m u qt m qtgt
q m m
m u m qt m qtut
q m m
= − = − −
− −= − − − −
−= − − + −
− −= − + − − −
∫
2
20 0
0
1ln
2
gt
m u m qtut ut gt
q m
−= + − −
20 0
0
1ln
2
m mh u t t gt
q m qt
= − − − −
(2)
Data: 2
0960 kg, 10 kg/s, 3600 m/s, 9.81 m/sm q u g= = = =
fuel
fuel
800800 kg, 80 s
10
mm t
q= = = =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(a) ( )( )2 3960 960 13600 80 80 ln 9.81 80 153.4 10 m
10 960 800 2h
= − − − = × −
153.4 kmh =
(b) From equation (1), ( )( )9603600ln 9.81 80
960 800v = −
−
5670 m/s=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 104.
Data from Problem 14.97: 0
5000 kg, 4200 m/sm u= =
0 0
0, 0v s= =
Thrust force dm
P u uqdt
= =
Mass of satellite plus unspent fuel 0
m m qt= −
Acceleration: 0
P uqa
m m qt= =
−
Integrating with respect to time to obtain the velocity,
0 00 0
0
t t qv v adt v u dt
m qt= + = +
−∫ ∫ (1)
( ) 0
0 0 0 0
0
ln ln lnm qt
v u m qt m v um
− = − − − = −
Integrating again to obtain the displacement,
0
0 0 0
0
lnt m qt
s s v t u dtm
−= + − ∫
Let 0 0
0 0
or
m qt q mz dz dt dt dz
m m q
−= = − = −
( ) ]0 0
0 0
0 0
00 0 0 0
0 0
0 0 0 0
0 0
0 0
0
0 0 0
0 0
0 0
ln ln
ln 1 ln 1
1 ln 1 1
ln 1 1 ln 1
zz
z z
o
m u m us s v t zdz z z z
q q
mm u m qt m qt ms v t
q m m m m
m u qt m qts v t
q m m
m u m qt m qts v t ut
q m m
= + + = −
− −= + + − − −
−= + + − − +
− −= + + − + − −
∫
0 0
0 0
0
lnm u m qt
s v t ut utq m
−= + + + −
0 0
0 0
0
lnm m
s s v t u t tq m qt
= + + − − −
(2)
Using the data,
( )( )5000 5000
0 0 4200 80 80 ln18.75 5000 18.75 80
s
= + + − − −
356.367 10 m= × 56.4 kms =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 105.
Let F be the thrust force, and dm
dt be the mass flow rate.
Absolute velocity of exhaust: ev u v= −
Thrust force: ( )dmF u v
dt= −
Power of thrust force: ( )1
dmP Fv u v v
dt= = −
Power associated with exhaust: ( ) ( ) ( )( )22
2
1 1
2 2e
P t m v m u v∆ = ∆ = ∆ −
( )22
1
2
dmP u v
dt= −
Total power supplied by engine: 1 2
P P P= +
( ) ( ) ( )2 2 21 1
2 2
dm dmP u v v u v u v
dt dt
= − + − = −
Mechanical efficiency: 1useful power
total power
P
Pη = =
( )2 2
2 u v v
u v
η−
=−
( )2v
u v
η =+
1η = when .u v= The exhaust, having zero velocity, carries no power away.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 106.
Let F be the thrust force and dm
dt be the mass flow rate.
Absolute velocity of exhaust: ev u v= −
Thrust force: dm
F udt
=
Power of thrust force: 1
dmP Fv uv
dt= =
Power associated with exhaust: ( ) ( ) ( )( )22
2
1 1
2 2e
P t m v m u v∆ = ∆ = ∆ −
( )22
1
2
dmP u v
dt= −
Total power supplied by engine: 1 2
P P P= +
( ) ( )2 2 21 1
2 2
dm dmP uv u v u v
dt dt
= + − = +
Mechanical efficiency: 1useful power
total power
P
Pη = =
( )2 2
2uv
u v
η =+
1η = when .u v= The exhaust, having zero velocity, carries no power away.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 107.
The weights are 30 lb, 40 lb, and 50 lb.A B C
W W W= = =
Initial velocities: ( )0
9 ft/sAv = , ( )
06 ft/s
Bv = , ( )
0and 0.
Cv =
There are no horizontal external forces acting during the impacts, and the baggage carrier is free to coast
between the impacts.
(a) Suitcase A is thrown first.
Let 1v be the common velocity of suitcase A and the carrier after the first impact and
2v be the common
velocity of the two suitcases and the carrier after the second impact.
Initial momenta: ( ) ( )0 0, , and 0.A B
A B
W Wv v
g g
Suitcase A impacts carrier. Conservation of momentum:
( ) ( ) ( )( )0
1 10
30 90 3.375 ft/s
80
A AA A C
A
A C
W vW W Wv v v
g g W W
++ = = = =+
Suitcase B impacts on suitcase A and carrier. Conservation of momentum:
( ) 1 20
B A C A B C
B
W W W W W Wv v v
g g g
+ + ++ =
( ) ( ) ( )( ) ( )( )10
2
40 6 80 3.3754.25 ft/s
120
B B A C
A B C
W v W W vv
W W W
+ + += = =
+ + 24.25 ft/s=v
(b) Suitcase B is thrown first.
Let 3v be the common velocity of suitcase B and the carrier after the first impact and
4v be the common
velocity of all after the second impact.
Suitcase B impacts the carrier. Conservation of momentum:
( ) ( ) ( )( )0
3 30
40 60 2.6667 ft/s
90
B BB B C
B
B C
W vW W Wv v v
g g W W
++ = = = =+
Suitcase A impacts on suitcase B and carrier. Conservation of momentum:
( ) 3 40
A B C A B C
A
W W W W W Wv v v
g g g
+ + ++ =
( ) ( ) ( )( ) ( )( )30
4
30 9 90 2.66674.25 ft/s
120
A A B C
A B C
W v W W vv
W W W
+ + += = =
+ + 44.25 ft/s=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 108.
The weights are 30 lb, ?, and 50 lb.A B C
W W W= = =
Initial velocities: ( ) ( )0 0
7.2 ft/sA Bv v= = ( )
0, 0
Cv =
Final velocity: 3.6 ft/sfv =
(a) Conservation of momentum:
( ) ( )0 0
0A B A B C
A B f
W W W W Wv v v
g g g
+ ++ + = (1)
( )( ) ( ) ( )( )30 7.2 7.2 30 50 3.6B B
W W+ = + +
20.0 lbB
W =
(b) Equation (1) shows that the final velocity is independent of the order in which the suitcases are thrown.
3.60 ft/sf =v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 109.
Linear momentum of each particle expressed in kg m/s.⋅
12 6 6
8 6
8 16 8
A A
B B
C C
m
m
m
= + += += − + +
v i j k
v i j
v i j k
Position vectors, (meters): 3 , 1.2 2.4 3 , 3.6A B C
= = + + =r j r i j k r i
( )2Angular momentum about , kg m /s .O ⋅
( ) ( ) ( )
( ) ( ) ( )
0 3 0 1.2 2.4 3 3.6 0 0
12 6 6 8 6 0 8 16 8
18 36 18 24 12 28.8 57.6
0 4.8 9.6
O A A A B B B C C Cm m m= × + × + ×
= + +−
= − + − + − + − +
= − +
H r v r v r v
i j k i j k i j k
i k i j k j k
i j k
( ) ( )2 24.80 kg m /s 9.60 kg m /sO
= − ⋅ + ⋅H j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 110.
Position vectors, (meters): 3 , 1.2 2.4 3 , 3.6A B C
= = + + =r j r i j k r i
( ) Mass center:a ( )A B C A A B B C Cm m m m m m+ + = + +r r r r
( )( ) ( )( ) ( )( )9 3 3 2 1.2 2.4 3 4 3.6
1.86667 1.53333 0.66667
= + + + +
= + +
r j i j k i
r i j k
( ) ( ) ( )1.867 m 1.533m 0.667 m= + +r i j k
Linear momentum of each particle, ( )2kg m /s .⋅
12 6 6
8 6
8 16 8
A A
B B
C C
m
m
m
= + += += − + +
v i j k
v i j
v i j k
(b) Linear momentum of the system, ( )kg m/s.⋅
12 28 14A A B B C C
m m m m= + + = + +v v v v i j k
( ) ( ) ( )12.00 kg m/s 28.0 kg m/s 14.00 kg m/sm = ⋅ + ⋅ + ⋅v i j k
Position vectors relative to the mass center, (meters).
1.86667 1.46667 0.66667
0.66667 0.86667 2.33333
1.73333 1.53333 0.66667
A A
B B
C C
′ = − = − + −′ = − = − + +′ = − = − −
r r r i j k
r r r i j k
r r r i j k
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
(c) Angular momentum about G, ( )2kg m /s .⋅
( ) ( )( )
1.86667 1.46667 0.66667 0.66667 0.86667 2.33333
12 6 6 8 6 0
1.73333 1.53333 0.66667
8 16 8
12.8 3.2 28.8 14 18.6667 10.9333
1.6 8.5333 15.4667
2.8 13.3333
G A A A B B B C C Cm m m′ ′ ′= × + × + ×
= − − + −
+ − −−
= + − + − + −
+ − − +
= − + −
H r v r v r v
i j k i j k
i j k
i j k i j k
i j k
i j 24.2667k
( ) ( ) ( )2 2 22.80 kg m /s 13.33 kg m /s 24.3 kg m /sG
= − ⋅ + ⋅ − ⋅H i j k
( ) ( ) ( )2 2 2
1.86667 1.53333 0.66667
12 28 14
2.8 kg m /s 18.1333 kg m /s 33.8667 kg m /s
m× =
= ⋅ − ⋅ + ⋅
i j k
r v
i j k
( ) ( )2 24.8 kg m /s 9.6 kg m /sG
m+ × = − ⋅ + ⋅H r v j k
Angular momentum about O.
( ) ( ) ( )
( ) ( ) ( )( ) ( )2 2
0 3 0 1.2 2.4 3 3.6 0 0
12 6 6 8 6 0 8 16 8
18 36 18 24 12 28.8 57.6
4.8 kg m /s 9.6 kg m /s
O A A A B B B C C Cm m m= × + × + ×
= + +−
= − + − + − + − +
= − ⋅ + ⋅
H r v r v r v
i j k i j k i j k
i k i j k j k
j k
Note that
O Gm= + ×H H r v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 111.
Choose x axis pointing east, y axis north, and z axis vertical.
Velocities before collision:
( )0
5.5 mi 5280 ft/miHelicoptor: 121 ft/s
4 min 60 s/minHv = ⋅ =
( )0
10 mi 5280 ft/miAirplane: 220 ft/s
4 min 60 s/minA xv = ⋅ =
( )0
7.5 mi 5280 ft/mi165 ft/s
4 min 60 s/minA yv
= − ⋅ = −
( ) ( ) ( ) ( ) ( )
( ) ( )
0 0 0 0
Mass center:
6000 3000121 220 165
9000 9000
154 ft/s 55 ft/s
H AH A Ax y
A H A H
m m
v v v
m m m m
= + + + +
= + −
= −
v i i j
i i j
i j
No external forces act during impact. Assume that only gravity acts after the impact. Motion of mass center
after impact:
( )2 2
0 0
1154 55 3600 16.1
2t z gt t t t
= + − = − + −
r v k i j k
Time of fall. 2 3600
14.953 s16.1
t t= =
( )( ) ( )( ) ( ) ( )154 14.953 55 14.953 2302.8 ft 822.42 ft= − = −r i j i j
( ) ( ) ( ) ( ) ( )1 1 2 2H A H H H H A A
m m m m m+ = + +r r r r
( ) ( ) ( ) ( ) ( )
( )( )
( )( ) ( )( )
1 1 2 2
1
19000 2302.8 822.42
3000
2000 1500 300 4000 1800 1500
A H A H H H H
A
m m m m
m
= + − −
= −
− − − −
r r r r
i j
i j i j
( ) ( )3510 ft 267 ft= −i j
( )Coordinates of point : 3510 ft, 267 ftA −
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 112.
Choose x axis pointing east, y axis north, and z axis vertical.
Velocities before collision:
( )0
5.5 mi 5280 ft/miHelicoptor: 121 ft/s
4 min 60 s/minHv = ⋅ =
( )0
10 mi 5280 ft/miAirplane: 220 ft/s
4 min 60 s/minA xv = ⋅ =
( )0
7.5 mi 5280 ft/mi165 ft/s
4 min 60 s/minA yv
= − ⋅ = −
( ) ( ) ( ) ( ) ( )
( ) ( )
0 0 0 0
Mass center:
6000 3000121 220 165
9000 9000
154 ft/s 55 ft/s
H AH A Ax y
A H A H
m m
v v v
m m m m
= + + + +
= + −
= −
v i i j
i i j
i j
No external forces act during impact. Assume that only gravity acts after the impact. Motion of mass center
after impact:
( )2 2
0 0
1154 55 3600 16.1
2t z gt t t t
= + − = − + −
r v k i j k
Time of fall. 2 3600
14.953 s16.1
t t= =
( )( ) ( )( ) ( ) ( )154 14.953 55 14.953 2302.8 ft 822.42 ft= − = −r i j i j
( ) ( ) ( ) ( ) ( )1 1 2 2H A H H H H A A
m m m m m+ = + +r r r r
( ) ( ) ( ) ( ) ( )
( )( )
( )( ) ( )( )
2 1 1
2
1
19000 2302.8 822.42
4000
3000 3600 240 2000 1200 600
H H A A A H H
H
r m m m m
m
= + − −
= −
− + − −
r r r
i j
i j i j
( ) ( )1881 ft 1730 ft= −i j ( )2
Coordinates of point : 1881 ft, 1730 ftH −
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 113.
Use a frame of reference moving with the mass center.
Conservation of momentum:
0A A B B
B
A B
A
m v m v
m
v v
m
′ ′= − +
′ ′=
Conservation of energy:
( ) ( ) ( )
( ) ( )
( )
2
2 2 2
2
1 1 1 1
2 2 2 2
2
2
B
A A B B A B B B
A
B A B
B
A
A
B
B A B
mV m v m v m v m v
m
m m mv
m
m Vv
m m m
′ ′ ′ ′= + = +
+′=
′ =+
Data: 2 25 30.15528 lb s /ft, 0.09317 lb s /ft
32.2 32.2A B
m m= = ⋅ = = ⋅
90 ft lbV = ⋅
( )( )( )( )( )
2 0.15528 9034.75 34.75 ft/s
0.09317 0.24845B Bv v′ ′= = = 30°
( )0.0931734.75 20.85 20.85 ft/s
0.15528A Av v′ ′= = = 30°
Velocities of A and B:
[24 ft/sA
=v ] [20.85 ft/s+ ]30° 12.00 ft/sA
=v 60.3°
[24 ft/sB
=v ] [34.75 ft/s+ ]30° 56.8 ft/sB
=v 17.8°
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 114.
Locate the mass center.
Let l be the distance between A and B.
( )B A B Am l m m l= +
2
7
5
7
B
A
A B
B
ml l l
m m
l l
= =+
=
(a) Linear momentum.
( )( )02.5 3.5 8.75
AL m v= = = 8.75 kg m/s= ⋅L
Angular momentum about G:
( )( )( )0 0
2 20.210 2.5 3.5 0.525
7 7G A A A
H l m v lm v= = = =
20.525 kg m /s
G= ⋅H
(b) There are no resultant external forces acting on the system;
therefore, L and G
H are conserved.
:L A A B B
m v m v L+ = 2.5 1.0 8.75A Bv v+ = (1)
:G
H B B B A A A Gl m v l m v H− =
( )( ) ( )( )5 20.210 1.0 0.210 2.5 0.525
7 7B Av v− =
0.15 0.15 0.525B Av v− = (2)
Solving (1) and (2) simultaneously, 1.5 m/s, 5 m/sA Bv v= =
1.500 m/sA
=v
5.00 m/sB
=v
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 115.
For steady flow 1 2
Q Q Q+ = (1)
Assume that the fluid speed is constant.
Velocity vectors: ( ) 1 2sin cos , , v v vθ θ= − = − =v i j v i v i
Let Pj be the force that plate C exerts on the fluid.
Impulse-momentum principle:
( ) ( ) ( ) ( )1 21 2m P t m m∆ + ∆ = ∆ + ∆v j v v
( ) ( )
1 2
1 2
m m mP
t t t
∆ ∆ ∆= + −∆ ∆ ∆
j v v v
( ) ( ) ( )1 2
sin cosdm dm dm
v v v vdt dt dt
θ θ = − + − −
i i i j
( )1 2sin cosQ v Q v Qvρ ρ ρ θ θ= − + − −i i i j
Resolve into components.
i: 1 2 2 1
0 sin sinQ v Q v Qv Q Q Qρ ρ ρ θ θ= − + − = − (2)
j: cosP Qvρ θ= (3)
Data: 2 462.41.93789 lb s /ft , 90 ft/s
32.2v
g
γρ = = = ⋅ =
3 3 3 3
1 226 gal/min 57.932 10 ft /s, 130 gal/min 289.66 10 ft /sQ Q− −= = × = = ×
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
From (1), 3 3347.59 10 ft /sQ −= ×
(a) From (2), 2 1sin 0.66667 41.810
Q Q
Qθ θ−= = = °
41.8θ = °
From (3), ( )( )( )31.93789 347.59 10 90 cos 41.810 45.2 lb.P
−= × ° =
(b) Force that stream exerts on plate C:
45.2 lbP− =j
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 116.
Calculation of or .
m dm
t dt
∆∆
mass density volume density area length= × = × ×
( ) ( ) mm A l Av t Av
tρ ρ ρ∆∆ = ∆ = ∆ =
∆
3 2
2 2 2
62.4 lb/ft 1.5 in60 ft/s 1.21118 lb s/ft
32.2 ft/s 144 in /ft
dmAv
dtρ= = ⋅ ⋅ = ⋅
Apply the principle of impulse-momentum.
moments about D: ( ) ( ) ( ) ( )12 16 10 4
12 12 12 12A B
m v C t W t m v − ∆ − ∆ + ∆ = − ∆
( )16 10 4 12B A
mC W v v
t
∆= + −∆
( )( ) ( ) ( )( ) ( )( )10 10 1.21118 4 60 12 60 481.37 = + − = −
30.085 lbC = − 30.1 lb=C
x components: ( ) ( ) ( )A x Bm v D t m v∆ + ∆ = ∆
( ) ( ) ( )( )1.21118 60 60 0x B A B A
m dmD v v v v
t dt
∆= − = − = − =∆
0x
D =
y components: ( ) ( ) ( )0 0y
C t D t W t+ ∆ + ∆ − ∆ =
( )10 30.085 40.085 lby
D W C= − = − − = 40.1 lb=D
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 117.
Calculation of dm
dt at a section in the airstream:
mass density volume density area length= × = × ×
( )m A l Av tρ ρ∆ = ∆ = ∆
m dm
Avt dt
ρ∆ = =∆
(a) ( )ThrustB A
dm
dt= −v v where
Bv is the velocity just downstream
of propeller and A
v is the velocity far upstream. Assume A
v is
negligible.
( ) 2 2Thrust
4Av v D v
πρ ρ = =
( ) ( )2 2 23600 1.21 2 3.801
4v v
π = =
30.774m/sv = 30.8 m/sv =
(b) ( ) ( )2212 30.774
4 4
dmQ Av D v
dt
π πρ
= = = =
3
96.7 m /sQ =
(c) Kinetic energy of mass :m∆
( ) ( ) ( )2 2 21 1 1
2 2 2T m v A l v Av t vρ ρ∆ = ∆ = ∆ = ∆
3 2 31 1
2 2 4
T dTAv D v
t dt
πρ ρ∆ = = = ∆
( ) ( ) ( )2 3 311.21 2 30.774 55.4 10 N m/s
2 4
π = = × ⋅
55.4 kWdT
dt=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr.,
Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell
© 2007 The McGraw-Hill Companies.
Chapter 14, Solution 118.
From Eq. (14.44) of the text book, the thrust is
( )( ) 3 2 310 kg/s 3600 m/s 36 10 kg m/s 36 10 Ndm
P udt
= = = × ⋅ = ×
F maΣ =
P mg ma− = P
a gm
= − (1)
(a) At the start of firing, 2
0960 kg, 9.81 m/s m m g= = =
From (1), 3
236 109.81 27.69 m/s
960a
×= − = 227.7 m/s=a
(b) As the last particle of fuel is consumed,
960 800 160 kg,m = − = ( )29.81 m/s assumedg =
From (1), 3
236 109.81 215.19 m/s
160a
×= − = 2215 m/s=a
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 1.
5.4 kg, 600 mm 0.6m, 300 mm 0.3 mm a b= = = = =
Total length of rod. 2 2 1.8 ml a b= + =
Mass per unit length. 5.4
3 kg/m1.8
m
lρ = = =
Use principal axes ,x z′ ′ as shown.
tan 0.5 26.565b
aβ β= = = °
10 cos rad/s 0x yω β ω′ = =
10 sin rad/szω β′ = −
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Moments of Inertia:
Part , kgm 2, kg mxI ′ ⋅ 2, kg mzI ′ ⋅
1.8aρ = 2
0.04052
bm =
210.054
12ma =
0.9bρ = 210.00675
12mb =
2
0.0812
am =
1.8aρ = 2
0.04052
bm =
210.054
12m a =
0.9bρ = 210.00675
12mb =
2
0.0812
am =
Σ 5.4lρ = 0.0945xI ′ = 0.270zI ′ =
Angular momentum .GH G x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +′ ′ ′H i j k
( )( ) ( )( )0.0945 10 cos 0 0.270 10 sinG β β′ ′= + + −H i k
( ) ( ) ( ) ( )0.945cos cos sin 2.70sin sin cosβ β β β β β= + + − − +i k i k
( ) ( )2 20.945 cos 2.70sin 0.945 2.70 sin cosβ β β β= + + −i k
1.296 0.702= −i k
( ) ( )2 21.296 kg m /s 0.702 kg m /sG = ⋅ − ⋅H i k !
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Chapter 18, Solution 2.
Use principal axes , y z′ ′ as shown.
cos 45 , sin 45y zω ω ω ω′ ′= ° = °
0xω ′ =
2 21 1,
3 12x yI ma I ma′ ′= =
25
12z x yI I I ma′ ′ ′= + =
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +H i j k
( ) ( )2 21 50 cos 45 sin 45
12 12ma maω ω ′ ′= + ° + °
j k
( )( )21cos 45 cos 45 sin 45
12A ma ω = ° ° − °
H j k
( )( )25sin 45 sin 45 cos 45
12ma ω + ° ° + °
j k
( )2
3 212
ω= +H j kAma
!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 3.
23.60.1118 lb s /ft 24 in. 2 ft
32.2m l= = ⋅ = =
( )( )1200 2125.664 rad/s
60
πω = =
Use principal axes , x y′ ′ as shown.
sin 20 42.980 rad/sxω ω′ = − ° = −
cos 20 118.085 rad/syω ω′ = ° =
For the rod, 0′ ≈xI
( )( )22 21 10.1118 2 0.037267 lb s ft
12 12yI ml′ = = = ⋅ ⋅
G x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +H i j k
( )( )0 0.037267 118.085 0′= + +j
4.40068 ′= j
( )4.40068 sin20 cos 20= ° + °i j
1.5051 4.1353= +i j
( ) ( )1.505 lb s ft 4.14 lb s ftG = ⋅ ⋅ + ⋅ ⋅H i j!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 4.
Use principal axes as shownx , y ,z .′ ′ ′
cos sinβ β′ = +i i j
sin cosβ β= − +′j i j
cos sinβ β′ ′= −i i j
sin cosβ β′ ′= +j i j
cos sinω ω β ω β= = −′ ′i i jωωωω
Pr incipal moments of inertia:
2 21 1,
2 4x y zI mr I I mr′ ′ ′= = =
Angular momentum:
G x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +H i j k
2 21 1cos sin
2 4mr mrω β ω β′ ′= −i j
( ) ( )2 21 1cos cos sin sin sin cos
2 4G mr mrω β β β ω β β β = + − − + H i j i j
2 2 2 21 1 1cos sin sin cos
2 4 4mr mrω β β ω β β = + +
i j
For 20 ,β = ° ( ) ( )2 20.47076 0.080348G mr mrω ω= +H i j
( )( )
0.080348tan
0.47076
G y
G x
H
Hθ = =
9.7θ = ° !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 5.
Body diagonal: ( )22 22 6= + + =d a a a a
( ) 226 6 6
a a adω ω ω ω= − + − = − + −ω i j k i j k
( )2 2 21 5212 12xI m a a ma = + =
2 2 21 112 6yI m a a ma = + =
( )22 21 5212 12zI m a a ma = + =
(a) G x x y y z zI I Iω ω ω= + +H i j k
2 2 25 1 2 512 6 126 6 6
ma ma maω ω ω = − + + −
i j k
( )2
5 4 512 6ma ω= − + −i j k
2 2
2 2 2 115 4 51212 6
ω ω= + + =Gma maH 20.276 ω=GH ma !
(b) ( )( ) ( ) ( )2 2
5 4 5 212 6
ω⋅ = − + − ⋅ − + −H ω i j k i j kGma
( )( )2 2
218 112 6 4
ω ω= =ma ma
2 21112GH maω ω=
12cos 0.904534 11
θω⋅= = =H ωG
GH 25.2θ = °!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 6.
Body diagonal ( )22 22 6= + + =d a a a a
( ) 226 6 6
ω ω ω ω= − + − = − + −ω i j k i j ka a ad
Total area ( )2 2 2 22 2 2 10= + + =a a a a
For each square plate: 110
′ =m m
2 2 2 21 13 1312 12 120xI m a m a m a ma′ ′ ′= + = =
2 21 16 60yI m a ma′= =
213120z xI I ma= =
For each plate parallel to the yz plane: 15
′ =m m
( )22 2 21 5 1212 12 12xI m a a m a ma ′ ′= + = =
2
2 2 21 1 112 2 3 15y
aI m a m m a ma ′ ′ ′= + = =
( )2
2 2 21 7 7212 2 12 60z
aI m a m m a ma ′ ′= + = =
For each plate parallel to the xy plane: 15
′ =m m
( )2
2 2 21 7 7212 2 12 60x
aI m a m m a ma ′ ′ ′= + = =
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2
2 2 21 1 112 2 3 15y
aI m a m m a ma ′ ′ ′= + = =
( )22 2 21 5 1212 12 12zI m a a m a ma ′ ′= + = =
Total moments of inertia:
2 213 1 7 372120 12 60 60xI ma ma = + + =
2 21 1 1 3260 15 15 10yI ma ma = + + =
2 213 7 1 372120 60 12 60zI ma ma = + + =
(a) ( )2
37 36 3760 6G x x y y z zmaI I I ωω ω ω= + + = − + −H i j k i j k
( ) ( ) ( )2
2 2 2 237 36 37 0.4321660 6
ω ω= + + =GmaH ma
20.432 ω=GH ma !
(b) ( )( ) ( ) ( )2
2 237 36 37 2 0.4055660 6Gma maω ω⋅ = − + − ⋅ − + − =H ω i j k i j k
0.40556cos 0.938440.43216
θω⋅= = =H ωG
GH
20.2θ = °!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 7.
( ) ( )2 1 4 rad/s 12 rad/sω ω= + = +ω j k j k
For axes , , x y z′ ′ ′ parallel to x, y, z with origin at A,
( )( )22 21 18 0.100 0.02 kg m
4 4xI mr′ = = = ⋅
2 20.02 kg m , 0.04 kg my x z x yI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +H i j k
( )( ) ( )( )0 0.02 4 0.04 12 0.08 0.48= + + = +j k j k
( ) ( )2 20.0800 kg m /s 0.480 kg m /sA = ⋅ + ⋅H j k!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 8.
( ) ( )1 2 8 rad/s 16 rad/sω ω= + = +ω j i i j
For axes , , x y z′ ′ ′ parallel to x, y, z with origin at A,
( )( )22 21 16 0.160 0.0384 kg m
4 4xI mr′ = = = ⋅
2 20.0384 kg m , 0.0768 kg mz x y x zI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +H i j k
( )( ) ( )( )0.0384 8 0.0768 16 0= + +i j
0.3072 1.2288= +i j
( ) ( )2 20.307 kg m /s 1.229 kg m /sA = ⋅ + ⋅H i j!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 9.
260 1.86335 lb s /ft, 2.4 in. 0.2 ft, 10 in. 0.83333 ft.32.2
= = ⋅ = = = =x ym k k
( )( )22 21.86335 0.2 0.074534 lb s ftx xI mk= = = ⋅ ⋅
( )( )22 21.86335 0.83333 1.29400 lb s fty z yI I mk= = = = ⋅ ⋅
( ) ( ) ( )G G G G x x y y z zx y zH H H I I Iω ω ω= + + = + +H i j k i j k
( ) 0.640 8.5867 rad/s
0.074534G x
xx
HI
ω = = =
( ) 0.018 0.013910 rad/s1.29400
G yy
y
H
Iω −= = = −
0zω =
sinω θ ω= −p y
0.013910 0.1596 rad/ssin sin 5
ωω
θ−
= = =°
yp
(a) Rate of spin. cosx s pω ω ω θ= +
coss x pω ω ω θ= −
8.5867 0.1596cos5= − °
8.43 rad/ssω = !
(b) Rate of precession. 0.1596 rad/spω = !
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Chapter 18, Solution 10.
2/
60 111.86335 lb s /ft, ft
32.2 12G Am = = ⋅ =
r i
cos sinv vθ θ= −v i j
/= + ×H H r vA G G A m
( )110.640 0.018 1950cos5 1950sin 5
12 = − + × ° − °
i j i i j
( )110.640 0.018 1950sin 5
12 = − − °
i j k
( ) ( ) ( )0.640 lb s ft 0.018 lb s ft 155.8 lb s ftA = ⋅ ⋅ − ⋅ ⋅ − ⋅ ⋅H i j k !
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Chapter 18, Solution 11.
Using Equation (18.11)
= × +H r v HO Gm
( ) ( ) 21 1
1
2 2ω ω = × + −
i k i j
rL mr mr
L
3
21 1 1
1 1
2 4
rmrL mr m
Lω ω ω= − + −j i j
( )2 2 21 1
1 1/
2 4ω ω = − +
H i jO mr m L r r L
which is the answer obtained in part b of Sample Problem 18.2.
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 12.
(a) Angular momenta HA and HB are related to HG and mv by
/ / and = × + = × +H r v H H r v HA G A G B G B Gm m
Subtracting, / /− = × − ×H H r v r vB A G B G Am m
( )/ /= + − ×H H r r vB A G B G A m
( )/ /= + + ×H r r vA G B A G m
/= + ×H H r vB A A B m
(b) It follows that =H HA B if, and only if
/ 0× =r vA B m
With points A and B located on the fixed axis, ω= λω
Where λ is a unit vector along the fixed axis, and
/ /ω= × = ×v r rG A G Aω λ
Then, ( )/ / 0ω× × =r rA B G Am λ
but, /rA B is parallel to λ, hence,
( )/ 0× × =rG Aλ λ
Let /G A= ×u rλ , so that 0.× =uλ
Note that u must be either perpendicular to λ or equal to zero. But, if u is perpendicular to λ, × uλ cannot be equal to zero.
Hence, / 0G A= × =u rλ
/rG A is parallel to λ and point G lies on the fixed axis.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 13.
( ) ( )2 1 4 rad/s 12 rad/sω ω= + = +ω j k j k
For axes , , x y z′ ′ ′ parallel to x, y, z with origin at A,
( )( )22 21 1 8 0.100 0.02 kg m4 4xI mr′ = = = ⋅
2 20.02 kg m , 0.04 kg my x z x yI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +H i j k
( )( ) ( )( ) ( ) ( )2 20 0.02 4 0.04 12 0.08 kg m /s 0.48 kg m /s= + + = ⋅ + ⋅j k j k
Point A is the mass center of the disk.
( ) ( )/ 0.32 m 0.2 mA O = −r i j
( ) ( )2 / 4 0.32 0.2 1.28 m/sA A Oω= = × = × − = −v v j r j i j k
( )( ) ( )8 1.28 10.24 kg m/sm = − = − ⋅v k k
( ) ( )/ 0.32 0.2 10.24A O m× = − × −r v i j k
( ) ( )2 22.048 kg m /s 3.2768 kg m /s= ⋅ + ⋅i j
/O A A O m= + ×H H r v
( ) ( ) ( )2 2 22.05 kg m /s 3.36 kg m /s 0.480 kg m /sO = ⋅ + ⋅ + ⋅H i j k !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 14.
( ) ( )2 1 8 rad/s 16 rad/sω ω= + = +ω i j i j
For axes , , x y z′ ′ ′ parallel to x, y, z with origin at A,
( )( )22 21 16 0.160 0.0384 kg m
4 4xI mr′ = = = ⋅
2 20.0384 kg m , 0.0768 kg mz x y x zI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +H i j k
( )( ) ( )( )0.0384 8 0.0768 16 0= + +i j
( ) ( )2 20.3072 kg m /s 1.2288 kg m /s= ⋅ + ⋅i j
Point A is the mass center of the disk.
( ) ( ) ( )/ 0.24 m 0.18 m 0.18 m= + −r i j kA D
( )2 / 8 0.24 0.18 0.18A A Dω= = × = × + −v v i r i i j k
( ) ( )1.44 m/s 1.44 m/s= +j k
( ) ( )8.64 kg m/s 8.64 kg m/sm = ⋅ + ⋅v j k
/ 0.24 0.18 0.18
0 8.64 8.64A D m× = −
i j k
r v
( ) ( ) ( )2 2 23.1104 kg m /s 2.0736 kg m /s 2.0736 kg m /s= ⋅ − ⋅ + ⋅i j k
/D A A D m= + ×H H r v
( ) ( ) ( )2 2 23.42 kg m /s 0.845 kg m /s 2.07 kg m /sD = ⋅ − ⋅ + ⋅H i j k!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 15.
5 kg, 200 mm 0.2 m= = =m a
( )( )2 36012 rad/s. 0, 0, 12 rad/s
60π
ω π ω ω ω π= = = = =x y z
Use parallel axes x′, y′, z′ with origin at the mass center as shown.
( )G xzxH I ω= −
( )G yzyH I ω= −
( )G zzH I ω=
Segments 1, 2, 3, and 4, each of mass 2.5 kg,′ =m contribute to , and .xz yz zI I I
Part xzI yzI zI
21
2′− m a 21
4′m a 21 1 1
12 4 ′+ +
m a
21
4′− m a 0 21
3′m a
21
4′− m a 0 21
3′m a
21
2′− m a 21
4′m a 21 1 1
12 4 ′+ +
m a
Σ 232
′− m a 212
′m a 2103
′m a
continued
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( ) 232G xH m a ω ′= − −
( )( ) ( )23 2.5 0.2 122
π =
25.6549 kg m /s= ⋅
( ) 212G yH m a ω ′= −
( )( ) ( )21 2.5 0.2 122
π = −
21.8850 kg m /s= − ⋅
( ) 2103G zH m a ω ′=
( )( ) ( )210 2.5 0.2 123
π =
212.5664 kg m /s= ⋅
Velocity of the mass center: 0=v
(a) /= + × =H H r v HA G G A Gm
( ) ( ) ( )2 2 25.65 kg m /s 1.885 kg m /s 12.57 kg m /s= ⋅ − ⋅ + ⋅H i j kA !
(b) ( ), = ⋅ = ⋅ =k H k HAB AB A A A zHλ λ
( ) ( ) ( )2 2 2 25.6549 1.8850 12.5664 13.9085 kg m /s= + + = ⋅AH
( ) 12.5664cos
13.9085θ = =A z
A
HH
25.4θ = °!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 16.
5 kg, 200 mm 0.2 m= = =m a
( )( )2 36012 rad/s. 0, 0, 12 rad/s
60π
ω π ω ω ω π= = = = =x y z
Use parallel axes x′, y′, z′ with origin at the mass center as shown.
( )G xzxH I ω= −
( )G yzyH I ω= −
( )G zzH I ω=
Segments 1, 2, 3, and 4, each of mass 2.5 kg,′ =m contribute to , and .xz yz zI I I
Part xzI yzI zI
21
2′− m a 21
4′m a 21 1 1
12 4 ′+ +
m a
21
4′− m a 0 21
3′m a
21
4′− m a 0 21
3′m a
21
2′− m a 21
4′m a 21 1 1
12 4 ′+ +
m a
Σ 232
′− m a 212
′m a 2103
′m a
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( ) 232G xH m a ω ′= − −
( )( ) ( )23 2.5 0.2 122
π =
25.6549 kg m /s= ⋅
( ) 212G yH m a ω ′= −
( )( ) ( )21 2.5 0.2 122
π = −
21.8850 kg m /s= − ⋅
( ) 2103G zH m a ω ′=
( )( ) ( )210 2.5 0.2 123
π =
212.5664 kg m /s= ⋅
Velocity of the mass center: 0=v
(a) /= + × =H H r v HB G G B Gm
( ) ( ) ( )2 2 25.65 kg m /s 1.885 kg m /s 12.57 kg m /s= ⋅ − ⋅ + ⋅H i j kB !
(b) ( ), = − ⋅ = − ⋅ = −k H k HBA BA A A A zHλ λ
( ) ( ) ( )2 2 2 25.6549 1.8850 12.5664 13.9085 kg m /s= + + = ⋅AH
( ) 12.5664cos
13.9085θ = − = −A z
A
HH
154.6θ = °!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 17.
2100.31056 lb s /ft
32.2
Wm
g= = = ⋅
( )12 rad/s , 0ω ω ω= = =i y z
( )G xxH I ω=
( )G xyyH I ω= −
( )G xzzH I ω= −
The shaft is comprised of 8 sections, each of length
10
ft 12
a = and of mass 20.03882 lb s /ft.8
mm′ = = ⋅
( ) ( )( ) ( )2
2 2 2 21 10 10 104 2 0.03882 0.089861 lb s ft
3 3 3 12xI m a m a m a ′ ′ ′= + = = = ⋅ ⋅
0xyI =
( ) ( )( )2
2 2104 2 2 0.03882 0.053916 lb s ft
2 12xza
I m a m a ′ ′= = = = ⋅ ⋅
( ) ( )( )0.089861 12 1.0783 lb s ftG xH = = ⋅ ⋅
( ) 0G yH =
( ) ( )( )0.053916 12 0.6470 lb s ftG zH = − = − ⋅ ⋅
(a) ( ) ( )1.078 lb s ft 0.647 lb s ftG = ⋅ ⋅ − ⋅ ⋅H i k!
( ) ( )2 21.0783 0.6470 1.2575 lb s ftGH = + = ⋅ ⋅
(b) ( )1.0783 0.6470 12 12.940 lb ftG ⋅ = − ⋅ = ⋅H i k iωωωω
( )( )12.940
cos 0.857521.2575 12
G
GHθ
ω⋅= = =H ωωωω
31.0θ = °!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 18.
2100.31056 lb s /ft
32.2
Wm
g= = = ⋅
( )12 rad/s , 0ω ω ω= = =i y z
( )G xxH I ω=
( )G xyyH I ω= −
( )G xzzH I ω= −
The shaft is comprised of 8 sections, each of length
10
ft 12
a = and of mass 20.03882 lb s /ft.8
mm′ = = ⋅
( ) ( )( ) ( )2
2 2 2 21 10 10 104 2 0.03882 0.089861 lb s ft
3 3 3 12xI m a m a m a ′ ′ ′= + = = = ⋅ ⋅
0xyI =
( ) ( )( )2
2 2104 2 2 0.03882 0.053916 lb s ft
2 12xza
I m a m a ′ ′= = = = ⋅ ⋅
( ) ( )( )0.089861 12 1.0783 lb s ftG xH = = ⋅ ⋅
( ) 0G yH =
( ) ( )( )0.053916 12 0.6470 lb s ftG zH = − = − ⋅ ⋅
( ) ( )1.078 lb s ft 0.647 lb s ftG = ⋅ ⋅ − ⋅ ⋅H i k
Since point G lies on the axis of rotation, its velocity is zero.
0G= =v v
(a) /= + × =H H r v HA G G A Gm
( ) ( )1.078 lb s ft 0.647 lb s ftA = ⋅ ⋅ − ⋅ ⋅H i k !
(b) /= + × =H H r v HB G G B Gm
( ) ( )1.078 lb s ft 0.647 lb s ftB = ⋅ ⋅ − ⋅ ⋅H i k !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 19.
Angular velocity: ω ω= j
Angular momentum about the mass center: G xy y yzI I Iω ω ω= − + −H i j k (1)
Since the body lies in the xy plane, 0.yzI =
Calculation of and : Letxy yI I 2
mass per unit area.m m
A abρ = = =
( ) ( )mass area.I Iρ=
For the pairs of area elements shown,
2el el2 2
2xyx
dI x y dA yxdy x ydy= = =
2
20 0
a axy
byI x ydy b ydy
a = = −
∫ ∫
2 2
2 2 320 0 0
2a a ab bb ydy y dy y dy
a a= − +∫ ∫ ∫
2 2 2 3 2 2 2 21 2 1 1
2 3 4 12b a b a b a b a= − + =
3 31 12
12 6yI ab ab = =
For mass, 21 1,
6 3xy yI mab I mb= =
Data: 8 kg, 750 mm 0.75 m, 6 rad/sm a b ω= = = = =
( )( )( ) 218 0.75 0.75 0.75 kg m
6xyI = = ⋅
( )( )2 218 0.75 1.50 kg m
3yI = = ⋅
From (1), ( ) ( )2 24.50 kg m /s 9.00 kg m /sG = − ⋅ + ⋅H i j!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 20.
Mass of each sheet 1.6
0.8 kg2
m = =
Required moment and products of inertia.
( ) ( )( )22 3 21 12 2 0.8 0.120 7.68 10 kg m
3 3xI mb − = = = × ⋅
( )( )( ) 3 20.8 0.080 0.060 3.84 10 kg m2 2xya b
I m − = − = − = − × ⋅
( )( )( ) 3 20.8 0.080 0.060 3.84 10 kg m2 2xza b
I m − = = = × ⋅
Angular velocity. 20 rad/s, 0x y zω ω ω= = =
Angular momentum about G.
( )G x x xy y xz zxH I I Iω ω ω= − −
( )( )3 27.68 10 20 0 0 0.1536 kg m /s−= × − − = ⋅
( )G xy x y y yz zyH I I Iω ω ω= − + −
( )( )3 23.84 10 20 0 0 0.0768 kg m /s−= − − × + − = ⋅
( )G xz x yz y z zzH I I Iω ω ω= − − +
( )( )3 23.84 10 20 0 0 0.0768 kg m /s−= − × − + = − ⋅
( ) ( ) ( )2 2 20.1536 kg m /s 0.0768 kg m /s 0.0768 kg m /sG = ⋅ + ⋅ − ⋅H i j k !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 21.
mass per unit length 1.2 kg/mρ = =
225 mm 0.225 m, 300 mm 0.3 m.r l= = = =
Moments and products of inertia: Formulas
m xI yI zI yzI
Upper ring 2 rπ ρ 2 2 21 12 4
m r r l + +
( )2 2m r r+ 2 21 12 4
m r l +
12
m rl −
Lower ring 2 rπ ρ 2 2 21 12 4
m r r l + +
( )2 2m r r+ 2 21 12 4
m r l +
12
m rl −
Rod AB lρ 2112
ml 0 2112
ml 0
Moments and products of inertia: Values
( )kgm ( )2kg mxI ⋅ ( )2kg myI ⋅ ( )2kg mzI ⋅ ( )2kg myzI ⋅
Upper ring 1.69646 0.166995 0.171767 0.081112 −0.057256
Lower ring 1.69646 0.166995 0.171767 0.081112 −0.057256
Rod AB 0.36 0.0027 0 0.0027 0
Totals 3.75292 0.336691 0.343533 0.164924 0.114511
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Impulse-momentum principle: Before impact, 0, 0G= =v H
(a) ( ) 5.4 3.75292
F tt m
m∆
∆ = = =F v v j
( )1.439 m/s=v j!
(b) Moments about G: /E G Gt× ∆ =r F H
( ) ( ) ( ) ( ) ( )0.225 0.15 0.225 5.4 G G Gx y zH H H− + × = + +i j k j i j k
( ) ( )1.215 1.215 x x y y yz z yz y z zI I I I Iω ω ω ω ω− + = + − + − +i k i j k
Substitute numerical values for moments and products of inertia and resolve into components.
: 1.215 0.336691 xω− =i
: 0 0.343533 0.114511y zω ω= +j
: 1.215 0.114511 0.164924y zω ω= +k
Solving, 3.6087 rad/s, 3.1952 rad/s, 9.5855 rad/sx y zω ω ω= − = − =
( ) ( ) ( )3.61 rad/s 3.20 rad/s 9.59 rad/s= − − +i j kω !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 22.
mass per unit length 1.2 kg/mρ = =
225 mm 0.225 m, 300 mm 0.3 m.r l= = = =
Moments and products of inertia: Formulas
m xI yI zI yzI
Upper ring 2 rπ ρ 2 2 21 12 4
m r r l + +
( )2 2m r r+ 2 21 12 4
m r l +
12
m rl −
Lower ring 2 rπ ρ 2 2 21 12 4
m r r l + +
( )2 2m r r+ 2 21 12 4
m r l +
12
m rl −
Rod AB lρ 2112
ml 0 2112
ml 0
Moments and products of inertia: Values
( )kgm ( )2kg mxI ⋅ ( )2kg myI ⋅ ( )2kg mzI ⋅ ( )2kg myzI ⋅
Upper ring 1.69646 0.166995 0.171767 0.081112 −0.057256
Lower ring 1.69646 0.166995 0.171767 0.081112 −0.057256
Rod AB 0.36 0.0027 0 0.0027 0
Totals 3.75292 0.336691 0.343533 0.164924 0.114511
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Impulse-momentum principle: Before impact, 0, 0G= =v H
(a) 5.4 3.75292
tt mm∆ −∆ = = =F iF v v
( )1.439 m/s= −v i!
(b) Moments about G: /E G Gt× ∆ =r F H
( ) ( ) ( ) ( ) ( )0.225 0.15 0.225 5.4 G G Gx y zH H H− + × − = + +i j k i i j k
( ) ( )1.215 0.81 x x y y yz z yz y z zI I I I Iω ω ω ω ω− − = + − + − +j k i j k
Substitute numerical values for moments and products of inertia and resolve into components.
: 0 0.336691 xω=i
: 1.215 0.343533 0.114511y zω ω− = +j
: 0.81 0.114511 0.164924y zω ω− = +k
Solving, 0, 2.4717 rad/s, 3.1952 rad/sx y zω ω ω= = − = −
( ) ( )2.47 rad/s 3.20 rad/s= − −j kω !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 23.
Total mass. 3m m m m+ + =
Moments and products of inertia.
2 2 21 1 1012 12 6xI md md md= + + =
2 2
2 2 21 1 22 12 12 2 3yd dI m md md m md = + + + =
2 2
2 2 21 1 212 2 12 2 3z
d dI md m md m md = + + + =
0yz zx xyI I I= = =
Angular momentum about mass center G.
G x x y y z zI I Iω ω ω= + +H i j k
Constraint of cable at G. 0yv =
Principle of impulse and momentum.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Linear momentum components.
: 0 3 xx mv= 0xv =
: 3 0yy F t T t mv− ∆ + ∆ = = T t F t∆ = ∆
2: 0 3z mv= 2 0v =
Angular momentum components.
( ) ( )2 2A Gd dF t F t × − ∆ = + × − ∆ =
r j i k j H
( ) ( )1 12 2 x x y y z zdF t dF t I I Iω ω ω∆ = − ∆ = + +i k i j k
( ) 21 1:2 6 xdF t md ω∆ =i ( )3
xF tmd
ω∆
=
22: 03 ymd ω=j 0yω =
( ) 21 2:2 3 zdF t md ω− ∆ =k ( )3
4zF t
mdω
∆= −
(a) Velocity of the mass center. x y zv v v= + +v i j k
0=v !
(b) Angular velocity. x y zω ω ω= + +ω i j k
3 34
F t F tmd md
∆ ∆ = −
ω i k !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 24.
Total mass. 3m m m m+ + =
Moments and products of inertia.
2 2 21 1 10
12 12 6xI md md md= + + =
2 2
2 2 21 1 2
2 12 12 2 3yd d
I m md md m md = + + + =
2 2
2 2 21 1 2
12 2 12 2 3zd d
I md m md m md = + + + =
0yz zx xyI I I= = =
Angular momentum about mass center G.
G x x y y z zI I Iω ω ω= + +H i j k
Constraint of cable at G. 0yv =
Principle of impulse and momentum.
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Linear momentum components.
: 0 3 xx mv= 0xv =
: 3 yy T t mv∆ = 0T t∆ =
: 3 zz F t mv− ∆ = 3zF t
vm
∆= −
Angular momentum components.
( ) ( )2 2B Gd d
F t F t × − ∆ = − + × − ∆ =
r k i j k H
( ) ( )1 1
2 2 x x y y z zdF t dF t I I Iω ω ω− ∆ − ∆ = + +i j i j k
( ) 21 1:
2 6 xdF t md ω− ∆ =i ( )3
x
F t
mdω
∆= −
( ) 21 2:
2 3 ydF t md ω− ∆ =j ( )3
y
F t
mdω
∆= −
22: 0
3 zmd ω=k 0zω =
(a) Velocity of the mass center. x y zv v v= + +v i j k
3
F t
m
∆ = −
v k !
(b) Angular velocity. x y zω ω ω= + +ω i j k
3 3
4
F t F t
md md
∆ ∆ = − −
ω i j!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 25.
Moments and products of inertia:
Part m xI yI yI xyI
OA 15 m
( )( )15
2 2 21 1 112 4 4
m
a a a× + +
( )( )15
2 2 21 112 4
m
a a a× + + ( )( )2 21 1
5 4m a a+ ( )( )21 15 2m a−
AB 15 m ( )( )21 1
5 4m a ( )( )21 15 3m a
( )( )15
2 2 21 1 112 4 4
m
a a a× + + ( )( )21 1
5 4m a−
BC 15 m ( )( )21 1
5 12m a 0 ( )( )21 15 12m a 0
CD 15 m ( )( )21 1
5 4m a ( )( )21 15 3m a
( )( )15
2 2 21 1 112 4 4
m
a a a× + + ( )( )21 1
5 4m a−
DE 15 m
( )( )15
2 2 21 1 112 4 4
m
a a a× + +
( )( )15
2 2 21 112 4
m
a a a× + + ( )( )2 21 1
5 4m a a+ ( )( )21 15 2m a−
Σ m 20.35ma 20.66667ma 20.75ma 20.3ma−
2 2 21 1 1 1 0.25 2 5 2xzI m a m a ma = + =
2 2 21 1 1 1 0.15 4 5 4yzI m a m a ma = − + − = −
Angular momentum about the mass center.
( ) 2 2 20.35 0.3 0.2G x x xy y xz z x y zxH I I I ma ma maω ω ω ω ω ω= − − = + −
( ) 2 2 20.3 0.66667 0.1G xy x y y yz z x y zyH I I I ma ma maω ω ω ω ω ω= − + − = + +
( ) 2 2 20.2 0.1 0.75G xz x yz z z z x y zzH I I I ma ma maω ω ω ω ω ω= − − + = − + +
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Constraint of the supporting cable: 0yv =
Impulse-momentum principle: Before impact, 0, 0.G= =v H
(a) Linear momentum: ( )t T t mv∆ + ∆ =F j Resolve into components.
0 , 0, 0x zmv F t T t mv= − ∆ + ∆ = =j
0, , 0x zv T t F t v= ∆ = ∆ = 0=v !
(b) Angular momentum, moments about G: /A G Gt× ∆ =r F H
( ) ( ) ( ) ( ) ( )2 G G Gx y za a F t aF t H H H − × − ∆ = ∆ = + +
j i j k i j k
Using expressions for ( ) ( ), ,G Gx yH H and ( )G zH and resolving into components,
2 2 2: 0 0.35 0.3 0.2x y zma ma maω ω ω= + −i
2 2 2: 0 0.3 0.66667 0.1x y zma ma maω ω ω= + +j
2 2 2: 0.2 0.1 0.75x y zaF t ma ma maω ω ω∆ = − + +k
Solving, ( ) ( ) ( )z2.5 , 1.454 , 2.19x y
F t F t F tma ma ma
ω ω ω∆ ∆ ∆
= = − =
( )2.50 1.454 2.19F tma
∆ = − +
i j kω !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 26.
Moments and products of inertia:
Part m xI yI yI xyI
OA 15 m
( )( )15
2 2 21 1 112 4 4
m
a a a× + +
( )( )15
2 2 21 112 4
m
a a a× + + ( )( )2 21 1
5 4m a a+ ( )( )21 15 2m a−
AB 15 m ( )( )21 1
5 4m a ( )( )21 15 3m a
( )( )15
2 2 21 1 112 4 4
m
a a a× + + ( )( )21 1
5 4m a−
BC 15 m ( )( )21 1
5 12m a 0 ( )( )21 15 12m a 0
CD 15 m ( )( )21 1
5 4m a ( )( )21 15 3m a
( )( )15
2 2 21 1 112 4 4
m
a a a× + + ( )( )21 1
5 4m a−
DE 15 m
( )( )15
2 2 21 1 112 4 4
m
a a a× + +
( )( )15
2 2 21 112 4
m
a a a× + + ( )( )2 21 1
5 4m a a+ ( )( )21 15 2m a−
Σ m 20.35ma 20.66667ma 20.75ma 20.3ma−
2 2 21 1 1 1 0.25 2 5 2xzI m a m a ma = + =
2 2 21 1 1 1 0.15 4 5 4yzI m a m a ma = − + − = −
Angular momentum about the mass center.
( ) 2 2 20.35 0.3 0.2G x x xy y xz z x y zxH I I I ma ma maω ω ω ω ω ω= − − = + −
( ) 2 2 20.3 0.66667 0.2G xy x y y yz z x y zyH I I I ma ma maω ω ω ω ω ω= − + − = + +
( ) 2 2 20.2 0.1 0.75G xz x yz z z z x y zzH I I I ma ma maω ω ω ω ω ω= − − + = − + +
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Constraint of the supporting cable: 0yv =
Impulse-momentum principle: Before impact, 0, 0.G= =v H
(a) Linear momentum: ( )t T t m∆ + ∆ =F j v Resolve in components.
0 , 0 0, x zm T t F t m= + ∆ = − ∆ =v v
0, 0, x zF tT Tm∆= ∆ = = −v v ( )/F t m= − ∆v k !
(b) Angular momentum, moments about G: /A G Gt× ∆ =r F H
( ) ( ) ( ) ( )12 2 G G Gx y za F t aF t H H H − × − ∆ = ∆ = + +
j k i i j k
Using expressions for ( ) ( ), ,G Gx yH H and ( )G zH and resolving into components,
2 2 21: 0.35 0.3 0.22 x y zaF t ma ma maω ω ω∆ = + −i
2 2 2: 0 0.3 0.66667 0.1x y zma ma maω ω ω= + +j
2 2 2: 0 0.2 0.1 0.75x y zma ma maω ω ω= − + +k
Solving, ( ) ( ) ( )3.75 , 1.875 , 1.25x y zF t F t F tm m ma
ω ω ω∆ ∆ ∆
= = − =
( )3.75 1.875 1.250F tma
∆ = − +
i j kω !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 27.
Moments and products of inertia:
m xI yI zI yzI
AB 14
m
2 2 21 1 14 12 4
m a a a + +
214
ma
21 14 3
m a
21 14 2
m a −
BC 12
m
( )21 1 22 12
m a
( )21 1 22 12
m a
0 0 0xyI =
CD 14
m
2 2 21 1 14 12 4
m a a a + +
214
ma
21 14 3
m a
21 14 2
m a −
0xzI =
Σ m 256
ma
223
ma
216
ma
214
ma−
Impulse-momentum principle: Before impact, 0, 0G= =v H
(a) ( )t m∆ =F v
tm∆= Fv F t
m∆ =
v i !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
(b) Moments about G: /A G Gt× ∆ =r F H
( ) ( ) ( ) ( ) ( )G G Gx y za a F t H H H− + × ∆ = + +j k i i j k
( ) ( ) ( ) ( )x x y y yz z yz y z zaF t aF t I I I I Iω ω ω ω ω∆ + ∆ = + − + − +j k i j k
Substitute expressions for moments and products of inertia and resolve into components.
25: 06 xma ω=i
2 22 1: 3 4y zaF t ma maω ω∆ = +j
2 21 1: 4 6y zaF t ma maω ω∆ = +k
Solving, ( ) ( )z0, 1.714 , 8.57x y
F t F tma ma
ω ω ω∆ ∆
= = − =
( )1.714 8.57F tma
∆ = − +
j kω !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 28.
Moments and products of inertia:
m xI yI zI yzI
AB 14
m
2 2 21 1 14 12 4
m a a a + +
214
ma
21 14 3
m a
21 14 2
m a −
BC 12
m
( )21 1 22 12
m a
( )21 1 22 12
m a
0 0 0xyI =
CD 14
m
2 2 21 1 14 12 4
m a a a + +
214
ma
21 14 3
m a
21 14 2
m a −
0xzI =
Σ m 256
ma
223
ma
216
ma
214
ma−
Impulse-Momentum Principle: Before impact, 0, 0G= =v H
(a) ( )t m∆ =F v
tm∆= Fv F t
m∆ =
v i !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
(b) Moments about G: /B G Gt× ∆ =r F H
( ) ( ) ( ) ( )G G Gx y za F t H H H× ∆ = + +k i i j k
( ) ( ) ( )x x y y yz z yz y z zaF t I I I I Iω ω ω ω ω∆ = + − + − +j i j k
Substitute expressions for moments and products of inertia and resolve into components.
25: 06 xma ω=i
2 22 1: 3 4y yaF t ma maω ω∆ = +j
2 21 1: 04 6y zma maω ω= +k
Solving, ( ) ( )z0, 3.43 , 5.14x y
F t F tma ma
ω ω ω∆ ∆
= = = −
( )3.43 5.14F tma
∆ = −
j kω !
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Chapter 18, Solution 29.
Point of impact: ( ) ( )2.7 m 0.225 mA = +r i k Initial linear momentum of the meteorite, ( )kg m/s :⋅
( )( )0 0.14 720 900 960 100.8 126 134.4m = − + = − +v i j k i j k
Its moment about the origin, ( )2kg m /s :⋅
0 2.7 0 0.225 28.35 340.2 340.2100.8 126 134.4
A m× = = − −−
i j kr v i j k
Final linear momentum of meteorite and its moment about the origin, ( ) ( )2kg m/s and kg m /s :⋅ ⋅
00.8 80.64 100.8 107.5m = − +v i j k
( )00.8 22.68 272.16 272.16A m× = − −r v i j k
Let AH be the angular momentum of the probe and m′ be its mass. Conservation of angular momentum about the origin for a system of particles consisting of the probe plus the meteorite:
( )0 00.8A A Am m× = + ×r v H r v
( ) ( ) ( )2 2 25.67 kg m /s 68.04 kg m /s 68.04 kg m /sA = ⋅ − ⋅ − ⋅H i j k
( ) ( )( )( )2 2
5.67, 0.012496 rad/s1500 0.55
A xx x A xx
x
HI H
m kω ω= = = =
′
( )( )
( )( )2 268.04 0.139612 rad/s
1500 0.57
A yy y A yy
y
HI H
m kω ω −= = = = −
′
( ) ( )( )( )2 2
68.04 0.18144 rad/s1500 0.50
A zz z A zz
z
HI H
m kω ω −= = = = −
′
( ) ( ) ( )0.0125 rad/s 0.1396 rad/s 0.1814 rad/s= − −i j kω !
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Chapter 18, Solution 30.
Point of impact: ( ) ( )2.7 m 0.225 mA = +r i k Initial linear momentum of the meteorite, ( )kg m/s :⋅
( )( )0 0.14 0.14 0.14 0.14x y z x y zm v v v v v v= + + = + +v i j k i j k
Its moment about the origin, ( )2kg m /s :⋅
( ) 00 2.7 0 0.2250.14 0.14 0.14
A A
x y z
mv v v
= × =i j k
H r v
( )0.0315 0.378 0.0315 0.378y z x yv v v v= − − − +i j k
Final linear momentum of the meteorite, ( )kg m/s :⋅
00.75 0.105 0.105 0.105x y zm v v v= + +v i j k
Its moment about the origin, ( )2kg m /s :⋅
( ) ( )00.75 0.023625 0.2835 0.023625 0.2835A y z x ym v v v v× = − − − +r v i j k
Initial linear momentum of the space probe, ( )kg m/s :⋅ 0 0m′ ′ =v
Final linear momentum of the space probe, ( )kg m/s :⋅
( ) ( )1500 0.017x y z y zm v v v v v′ ′ ′ ′ ′ ′+ + = − + +i j k i j k
Final angular momentum of space probe, ( )2kg m /s :⋅
( )2 2 2A x x y y z zm k k kω ω ω′= + +H i j k
( ) ( ) ( ) ( ) ( )2 2 21500 0.55 0.05 0.57 0.12 0.50 zω = + − +
i j k
22.6875 58.482 375 zω= − +i j k
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Conservation of linear momentum of the probe plus the meteorite, ( )kg m/s :⋅
0.14 0.14 0.14 0.105 0.105 0.105x y z x y zv v v v v v+ + = + +i j k i j k
( )( )1500 0.017 1500 1500y zv v′ ′+ − + +i j k
: 0.035 25.5xv = −i 728.57 m/sxv = −
: 0.035 1500y yv v′=j
: 0.035 1500z zv v′=k
Conservation of angular momentum about the origin, ( )2kg m /s :⋅
( )0.0315 0.378 0.0315 0.378y z x yv v v v− − − +i j k
( )0.023625 0.2835 0.023625 0.2835y z x yv v v v= − − − +i j k
22.6875 58.482 375 zω+ − +i j k
: 0.007875 22.6875yv− =i 2880.95 m/syv = −
: 0.0945 0.007875 58.482 0.083333 618.86 558.15 m/sz x z xv v v v− + = − = + =j
: 0.0945 375y zv ω− =k
(a) 6252 10z yvω −= − × 0.726 rad/szω = − !
(b) ( ) ( ) ( )0 729 m/s 2880 m/s 558 m/s= − − +v i j k !
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Chapter 18, Solution 31.
The disk is constrainted to rotate about the fixed point A. Point B of the disk does not rebound after the impact.
( ) 0B zv =
Kinematics. /B B A= ×v rω
( ) ( )0
B B x y zx zv va a
ω ω ω+ =−
i j ki k
( ) ( ), , 0 0B z B z x y x yx yv a v a a aω ω ω ω ω ω= − = = − − + = (1)
Moments of inertia:
2 2 2 2 2 2 21 5 1 1 3, , 4 4 4 2 2x y zI ma ma ma I ma I ma ma ma= + = = = + =
Impulse-momentum principle:
Moments about :A ( ) ( ) ( ) ( )0 1A Aa a B t+ − × ∆ =H i j k H
( ) ( )0y x x y y z zI aB t a B t I I Iω ω ω ω+ − ∆ − ∆ = + +j i j i j k
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Substitute values for , , and x y zI I I and resolve into components.
( ) 25: 04 xaB t ma ω− ∆ =i (2)
( )2 20
1 1: 4 4 yma aB t maω ω− ∆ =j (3)
23: 02 zma ω=k 0zω =
Solving (1), (2) and (3) simultaneously for , and ,x y B tω ω ∆
0 0 01 1 5, , 6 6 24x y B t maω ω ω ω ω= − = ∆ =
(a) Angular velocity: 0 01 16 6
ω ω= − +i jω !
(b) Velocity of mass center: /G G A= ×v rω
( )0 00
16 6 6G a aω ω ω = − + × − =
v i j j k
016G aω=v k !
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Chapter 18, Solution 32.
The disk is constrainted to rotate about the fixed point A. Point B of the disk does not rebound after the impact.
( ) 0B zv =
Kinematics. /B B A= ×v rω
( ) ( )0
B B x y zx zv va a
ω ω ω+ =−
i j ki k
( ) ( ), , 0 0B z B z x y x yx yv a v a a aω ω ω ω ω ω= − = = − − + = (1)
Moments of inertia:
2 2 2 2 2 2 21 5 1 1 3, , 4 4 4 2 2x y zI ma ma ma I ma I ma ma ma= + = = = + =
Impulse-momentum principle:
Moments about A: ( ) ( ) ( ) ( )0 1A Aa a B t+ − × ∆ =H i j k H
( ) ( )0y x x y y z zI aB t a B t I I Iω ω ω ω+ − ∆ − ∆ = + +j i j i j k
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Substitute values for , , and x y zI I I and resolve into components.
( ) 25: 04 xaB t ma ω− ∆ =i (2)
( )2 20
1 1: 4 4 yma aB t maω ω− ∆ =j (3)
23: 02 zma ω=k 0zω =
Solving (1), (2) and (3) simultaneously for , and ,x y B tω ω ∆
0 0 01 1 5, , 6 6 24x y B t maω ω ω ω ω= − = ∆ =
(a) Impulse at B: 00.208t maω∆ =Β k !
Velocity of the mass center: /G G A= ×v rω
( )0 0 01 1 16 6 6G a aω ω ω = = − + × − =
v v i j j k
(b) Linear momentum: ( )0m t B t m+ ∆ + ∆ =v A k v
( )0t m m B t∆ = − − ∆A v v k
0 0 01 506 24
ma maω ω= − −k k
0124
t maω∆ = −A k !
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Chapter 18, Solution 33.
Principal moments of inertia.
( )( )22 21200 1.120 1505.28 kg mx xI mk= = = ⋅
( )( )22 21200 1.200 1728 kg my yI mk= = = ⋅
( )( )22 21200 0.900 972 kg mz zI mk= = = ⋅
Initial angular velocity.
( ) ( ) ( )11 10.050 rad/s, 0, 0.075 rad/sω ω ω= = =x y z
Initial angular momentum.
( )1G x x y y z zI I Iω ω ω= + +H i j k
( ) ( )2 275.264 kg m / s 72.9 kg m /s= ⋅ + ⋅i k
Final angular momentum if ( )20.=ωωωω ( ) 0G z
=ΗΗΗΗ
Positions of jets A and B relative to mass center.
( ) ( )/ 1.2 m 1.8 m= +A Gr i k ( ) ( )/ 1.2 m 1.6 m= −B Gr i k
Impulses from jets A and B. ( ) ( )andA B
F t F t∆ ∆j j
Principle of impulse and momentum. Moments about G:
( ) ( ) ( ) ( )/ / G1G A G B GA B zF t F t+ × ∆ + × ∆ =H r j r j Η
( ) ( ) ( ) ( )75.264 72.9 1.2 1.8 1.2 1.6A B
F t F t+ + + × ∆ + − × ∆ = 0i k i k j i k j
( ) ( ) ( ) ( )75.264 +1.2 1.8 1.2 1.6 0+ 72.9 ∆ − ∆ + ∆ + ∆ =A A B B
F t F t F t F ti k k i k i
Components: i: ( ) ( )75.264 1.8 1.6 0A B
F t F t− ∆ + ∆ = (1)
k: ( ) ( )72.9 1.2 1.2 0A B
F t F t+ ∆ + ∆ = (2)
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Solving (1) and (2) simultaneously,
( ) 6.4518 N s,∆ = − ⋅A
F t ( ) 54.298 N s∆ = − ⋅B
F t
Since both impulse components are negative, the 50-N thrusts of jets A and B act in the negative y direction.
50 N= −F
(a) Operating times of jets.
( ) 6.4518
50
∆ −∆ = =−
AA
F tt
F 0.1290 sAt∆ = "
( ) 54.298
50
∆ −∆ = =−
BB
F tt
F 1.086 sBt∆ = "
Principle of impulse and momentum. Linear momentum:
( ) ( )A BF t F t m∆ + ∆ = ∆j j v
6.4518 54.298 1200− − = ∆j j v
( )310 m/s−∆ = − 50.6 ×v j
(b) Change in velocity of mass center. ( )50.6 mm/s∆ = −v j "
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Chapter 18, Solution 34.
Data from Problem 18.33.
Mass of satellite: 1200 kg.m =
Initial angular velocity: ( ) ( )0 0.050 rad/s 0.075 rad/s= +i jωωωω
Principal radii of gyration: 1.120 m, 1.200 m, 0.900 mx y zk k k= = =
Jet thrust 50 N= parallel to the y axis.
Principal moments of inertia.
( )( )22 21200 1.120 1505.28 kg mx xI mk= = = ⋅
( )( )22 21200 1.200 1728 kg my yI mk= = = ⋅
( )( )22 21200 0.900 972 kg mz zI mk= = = ⋅
Initial angular velocity.
( ) ( ) ( )11 10.050 rad/s, 0, 0.075 rad/sω ω ω= = =x y z
Initial angular momentum.
( )1G x x y y z zI I Iω ω ω= + +H i j k
( ) ( )2 275.264 kg m / s 72.9 kg m /s= ⋅ + ⋅i k
Final angular momentum if ( )20.x =ωωωω
( ) ( ) ( ) ( )22 2ω ω ω= + +G x x y y z zI I IH i j k
( ) ( )220 1728 972y zω ω= + +j k
Positions of jet B relative to mass center. ( ) ( )/ 1.2 m 1.6 m= −B Gr i j
Impulse from jet B. ( )BF t∆ j
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Principle of impulse and momentum. Moments about G:
( ) ( ) ( )/ G1 2G B G BF t+ × ∆ =H r j Η
( ) ( ) ( ) ( )2275.264 72.9 1.2 1.6 1728 972y zB
F t ω ω+ + − × ∆ = +i k i k j j k
( ) ( ) ( ) ( )2275.264 +1.2 1.6 1728 972ω ω+ 72.9 ∆ + ∆ = +y zB B
F t F ti k k i j k
Components: i: ( )75.264 1.6 0B
F t+ ∆ =
( ) 47.04 N s∆ = − ⋅B
F t
j: ( ) ( )2 2
0 1728 0y yω ω= =
k: ( ) ( )272.9 1.2 972 zB
F t ω+ ∆ =
( ) ( )( )2
72.9 1.2 47.040.01693 rad/s
972ω
+ −= =z
Since ( )BF t∆ is negative, the 50-N thrust of jet B acts in the negative y direction.
(a) Operating time of jet B.
( ) 47.04
50
∆ −∆ = =−
BB
F tt
F 0.941 sBt∆ = "
(b) Final angular velocity. ( ) ( ) ( )22 2x y zω ω ω= + +i j kωωωω
( )0.01693 rad/s= kωωωω "
Principle of impulse and momentum. Linear components:
( ) ( )BF t m∆ = ∆j v
47.04 1200− = ∆j v ( )0.0392 m/s∆ = −v j
(c) Change in velocity of mass center. ( )39.2 mm/s∆ = −v j "
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Chapter 18, Solution 35.
Principle of impulse-momentum:
Linear momentum: ( )0 x y zm C t m m m− + ∆ = + +v j j v i v j v k : 0 xmv=i 0xv =
0: ym C t mv− + ∆ =j v ( )0 yC t m v v∆ = + (1)
: 0 zmv=k 0zv =
Since the impact is perfectly plastic, ( ) 0.C yv =
( ) ( )/C G c G y x y zr v a cω ω ω= + × = + + + × −v v j i j k i kω
( ) ( ) ( )C C y y x z yx zv v c v c a aω ω ω ω+ = − + + + −i k i j k
: 0C x zv c aω ω+ + =j y x zv c aω ω= − − (2)
Moments about C: ( ) ( ) ( ) ( )0 0 G G G yx y zcmv amv H H ai c mv+ = + + + − + ×i k H i j k k j
( )2 2 2 22
2 2 23 3 3x y y ymc m c a ma mcv mavω ω ω= + + + − −i j k i k
20
1: 3 x ycmv mc mcvω= −i (3)
( )2 21: 03 ym c a ω= +j 0yω =
20
1: 3 z yamv ma mavω= −k (4)
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After using (2) to eliminate ,yv (3) and (4) become 043 x zc a vω ω+ =
043x zc a vω ω+ =
from which 0 03 3, 7 7x zc v a vω ω= =
03 1 17
vc a = +
i kω !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 36.
Principle of impulse-momentum:
Linear momentum: ( )0 x y zm C t m m m− + ∆ = + +v j j v i v j v k
: 0 xmv=i 0xv =
0: ymv C t mv− + ∆ =j ( )0 yC t m v v∆ = +
: 0 zmv=k 0zv =
Since the impact is perfectly plastic, ( ) 0.C yv =
( ) ( )/C G c G y x y zr v a cω ω ω= + × = + + + × −v v j i j k i kωωωω
( ) ( ) ( )C C y y x z yx zv v c v c a aω ω ω ω+ = − + + + −i k i j k
: 0C x zv c aω ω+ + =j y x zv c aω ω= − − (2)
Moments about C:
( ) ( ) ( ) ( )0 0 G G G yx y z
cmv amv H H ai c mv+ = + + + − + ×i k H i j k k j
( )2 2 2 22
2 2 2
3 3 3x y y ymc m c a ma mcv mavω ω ω= + + + − −i j k i k
20
1:
3 x ycmv mc mcvω= −i (3)
( )2 21: 0
3 ym c a ω= +j 0yω =
20
1:
3 z yamv ma mavω= −k (4)
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After using (2) to eliminate ,yv (3) and (4) become 04
3 x zc a vω ω+ =
04
3x zc a vω ω+ =
from which 0 03 3
, 7 7x zc v a vω ω= =
(a) Velocity of mass center:
From (2), 0 0 03 3 6
7 7 7yv v v v= − − = −
06
7v= −v j"
(b) Impulse at C:
From (1), ( )0 0 06
7yC t m v v m v v ∆ = + = −
01
7t mv∆ =C j"
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Chapter 18, Solution 37.
(a) ( ) ( )0 x x xy y xz z xy x y y yz zI I I I I Iω ω ω ω ω ω= − − + − + −H i j
( )xz x yz y z zI I Iω ω ω+ − − + k
x y zω ω ω= + +i j kω
2 20 x x xy y x xz z x xy x y y y yz z yI I I I I Iω ω ω ω ω ω ω ω ω ω⋅ = − − − + −H ω
2xz x z yz y z z zI I Iω ω ω ω ω− − +
( ) ( )2 2 212 2 2 22 x x y y z z xy x y yz y z xz x zI I I I I Iω ω ω ω ω ω ω ω ω = + + − − −
2T=
(b) 0 0 cosH ω θ⋅ =H ω
02 cosT H ω θ=
0
2cos TH
θω
=
But 00, 0, 0T H ω> > >
cos 0 90θ θ> < °
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Chapter 18, Solution 38.
(a) ( )2 2 21 2 2 22 x x y y z z xy x y yz y z xz x zT I I I I I Iω ω ω ω ω ω ω ω ω= + + − − −
Let cosx x xω ω θ ωλ= =
cosy y yω ω θ ωλ= =
cosz z zω ω θ ωλ= =
( )2 2 2 21 2 2 22 x x y y z z xy x y yz y z xz x zT I I I I I Iλ λ λ λ λ λ λ λ λ ω= + + − − −
212 OLI ω= 21
2 OLT I ω= !
(b) Each particle of mass ( )im∆ describes a circle of radius .iρ
The speed of the particle is i iv ρ ω=
Its kinetic energy is ( ) ( ) ( )2 2 21 12 2i i i iiT m v m ρ ω∆ = ∆ = ∆
The kinetic energy of the entire body is
( ) ( ) 2 212 i iiT T m ρ ω= Σ ∆ = Σ ∆
but ( ) 2OL i iI m ρ= Σ ∆
Hence, 212 OLT I ω= !
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Chapter 18, Solution 39.
From the solution of Prob. 18.1,
26.565β = °
20.0945 kg m / sxI ′ = ⋅ 20.270 kg m / szI ′ = ⋅
10cos 8.9443 rad/sxω β′ = =
0yω ′ =
10sin 4.4721 rad/szω β′ = − = −
Kinetic energy. 2 2 21 1 1
2 2 2x x y y z zT I I Iω ω ω′ ′ ′ ′ ′ ′= + +
( )( ) ( )( )2 21 10.0945 8.9443 0 0.270 4.4721
2 2= + + −T
6.48 J=T "
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Chapter 18, Solution 40.
Use principal axes , y z′ ′ as shown.
cos 45 , sin 45y zω ω ω ω′ ′= ° = °
0xω ′ =
2 21 1,
3 12x yI ma I ma′ ′= =
25
12z x yI I I ma′ ′ ′= + =
2 2 21 1 1
2 2 2x y zx y zT I I Iω ω ω′ ′ ′′ ′ ′= + +
( ) ( ) ( )2 22 2 21 1 1 1 1 50 cos 45 sin 45
2 3 2 12 2 12ma ma maω ω = + +
o o
2 2 2 21 50
48 48ma maω ω= + +
2 21
8T ma ω= "
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Chapter 18, Solution 41.
23.6 = 0.1118 lb s /ft 24 in. 2 ft
32.2m l= ⋅ = =
( )( )1200 2125.664 rad/s
60
πω = =
Use principal axes , x y′ ′ as shown.
sin 20 42.980 rad/sxω ω′ = − ° = −
cos 20 118.085 rad/syω ω′ = ° =
For the rod, 0xI ′ ≈
( )( )22 21 10.1118 2 0.037267 lb s ft
12 12yI ml′ = = = ⋅ ⋅
2 2 2 21 1 1 1
2 2 2 2x x y y z zT mv I I Iω ω ω′ ′ ′ ′ ′ ′= + + +
( )( )210 0 0.037267 118.085 0
2= + + +
260 ft lb= ⋅
260 ft lbT = ⋅ "
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Chapter 18, Solution 42.
Use principal axes , , as shown′ ′ ′x y z .
cos sinβ β′ = +i i j
sin cosβ β′ = − +j i j
cos sinβ β′ ′= −i i j
sin cosβ β′ ′= +j i j
cos sinω ω β ω β′ ′= = −i i jωωωω
cos sinω ω β ω ω β′ ′= = −x y
Pr incipal moments of inertia:
2 21 1,
2 4x y zI mr I I mr′ ′ ′= = =
Kinetic energy: 2 2 2 21 1 1 1
2 2 2 2x x y y z zT mv I I Iω ω ω′ ′ ′ ′ ′ ′= + + +
( ) ( )2 22 21 1 1 10 cos sin 0
2 2 2 4ω β ω β = + + − +
mr mr
( )2 2 2 212cos sin
8mr ω β β= +
20 ,For β = ° ( )2 2 212cos 20 sin 20
8ω ° + °T = mr
2 20.235T mr ω= "
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 43.
Body diagonal: ( )22 22 6d a a a a= + + =
( ) 22
6a a a
d
ω ω ω ω= − + − = − + −6 6
ω i j k i j k
( )2 2 21 52
12 12xI m a a ma = + =
2 2 21 1
12 6yI m a a ma = + =
( )22 21 52
12 12zI m a a ma = + =
Axis of rotation passes through the mass center, hence 0.=v
Kinetic energy: 2 2 2 21 1 1 1
2 2 2 2x y zx y zT mv I I Iω ω ω= + + +
2 2 22 2 2 2 21 5 1 1 2 1 5 1
02 12 2 6 2 12 86
T ma ma ma maω ω ω ω = + + + = 6 6
2 20.1250 T ma ω= "
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Chapter 18, Solution 44.
Body diagonal ( )22 22 6d a a a a= + + =
( ) 22
6a a a
d
ω ω ω ω= − + − = − + −6 6
ω i j k i j k
( )2 2 2 2Total area 2 2 2 10a a a a= + + =
For each square plate: 1
10m m′ =
2 2 2 21 13 13
12 12 120xI m a m a m a ma′ ′ ′= + = =
2 21 1
6 60yI m a ma′= =
213
120z xI I ma= =
For each plate parallel to the yz-plane: 1
5m m′ =
( )22 2 21 5 12
12 12 12xI m a a m a ma ′ ′= + = =
2
2 2 21 1 1
12 2 3 15ya
I m a m m a ma ′ ′ ′= + = =
( )2
2 2 21 7 72
12 2 12 60za
I m a m m a ma ′ ′= + = =
For each plate parallel to the xy plane: 1
5m m′ =
( )2
2 2 21 7 72
12 2 12 60xa
I m a m m a ma ′ ′ ′= + = =
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2
2 2 21 1 1
12 2 3 15ya
I m a m m a ma ′ ′ ′= + = =
( )22 2 21 5 12
12 12 12zI m a a m a ma ′ ′= + = =
Total moments of inertia:
2 213 1 7 372
120 12 60 60xI ma ma = + + =
2 21 1 1 32
60 15 15 10yI ma ma = + + =
2 213 7 1 372
120 60 12 60zI ma ma = + + =
Axis of rotation passes through the mass center, hence 0.=v
Kinetic energy: 2 2 2 21 1 1 1
2 2 2 2x y zx y zT mv I I Iω ω ω= + + +
2 2 22 2 21 37 1 3 2 1 37
02 60 2 10 2 60 6
T ma ma maω ω ω = + + + 6 6
2 273
360ma ω=
2 20.203 T ma ω= "
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 45.
( ) ( )2 1 4 rad/s 12 rad/sω ω= + = +ω j k j k
For axes , , x y z′ ′ ′ parallel to , , x y z with origin at A,
( )( )22 21 18 0.100 0.02 kg m
4 4xI mr′ = = = ⋅
2 20.02 kg m , 0.04 kg my x z x yI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
Point A is the mass center of the disk.
( ) ( )/ 0.32 m 0.2 mA O = −r i j
( ) ( )2 / 4 0.32 0.2 1.28 m/sA A Oω= = × = × − = −v v j r j i j k
1.28 m/sv =
Kinetic energy: 2 2 2 21 1 1 1
2 2 2 2x y zx y zT mv I I Iω ω ω′ ′ ′= + + +
( )( ) ( )( ) ( )( )2 2 21 1 18 1.28 0 0.02 4 0.04 12
2 2 2T = + + +
6.5536 0.16 2.88= + +
2 29.5936 kg m /s 9.5935 N m 9.5935 J= ⋅ = ⋅ =
9.59 JT = "
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Chapter 18, Solution 46.
( ) ( )2 1 8 rad/s 15 rad/sω ω= + = +ω i j i j
For axes , , x y z′ ′ ′ parallel to , , x y z with origin at A,
( )( )22 21 16 0.160 0.0384 kg m
4 4xI mr′ = = = ⋅
2 20.0384 kg m , 0.0768 kg mz x y x zI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
Point A is the mass center of the disk.
( ) ( )/ 0.18 m 0.18 mA C = −r j k
( )2 / 8 0.18 0.18A A Cω= = × = × −v v i r i j k
( ) ( )1.44 m/s 1.44 m/s= +j k
( ) ( )2 21.44 1.44 2.0365 m/sv = + =
Kinetic energy: 2 2 2 21 1 1 1
2 2 2 2x y zx y zT mv I I Iω ω ω′ ′ ′= + + +
( )( ) ( )( ) ( )( )2 2 21 1 16 2.0365 0.0384 8 0.0768 16 0
2 2 2T = + + +
12.4416 1.2288 9.8304= + +
2 223.5 kg m /s 23.5 N m 23.5 J= ⋅ = ⋅ =
23.5 JT = !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 47.
5 kg, 200 mm 0.2 mm a= = =
( )( )2 36012 rad/s.
60π
ω π= =
0, 0, 12 rad/sx y zω ω ω π= = =
Use parallel axes , ,x y z′ ′ ′ with origin at the mass center as shown.
2 2 21 1 12 2 2x zx y y z xy x y yz y z xz x zT I I I I I Iω ω ω ω ω ω ω ω ω= + + − − −
212 xI ω=
Part zI
21 1 1
12 4m a ′+ +
21
3m a′
21
3m a′
21 1 1
12 4m a ′+ +
Σ 2103
m a′
Segments 1, 2, 3, and 4, each of mass 2.5 kg,m′ = contribute to zI .
( )( )210 2.5 0.23zI =
20.33333 kg m= ⋅
( )( )21 0.33333 122
T π=
2 2237 kg m /s 237 N m= ⋅ = ⋅
237 JT = !
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Chapter 18, Solution 48.
210 0.31056 lb s /ft32.2
Wmg
= = = ⋅
( )12 rad/s , 0y zω ω ω= = =i
2 2 21 1 12 2 2x y zx y z xy x y yz y z xz x zT I I I I I Iω ω ω ω ω ω ω ω ω= + + − − −
12 xI ω 2=
The shaft is comprised of eight sections, each of length
10 ft12
a = and of mass 20.03882 lb s /ft.8mm′ = = ⋅
( ) ( )( ) ( )2
2 2 2 21 10 10 104 2 0.3882 0.089861 lb s ft3 3 3 12xI m a m a m a ′ ′ ′= + = = = ⋅ ⋅
( )( )21 0.089861 12 6.47 ft lb2
T = = ⋅
6.47 ft lbT = ⋅ !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 49.
Angular velocity: ( )= 6 rad/sω= j jωωωω
0, 6 rad/s, 0x y zω ω ω= = =
Velocity of mass center G. = 0.v
From the solution to Prob. 18.19, 21.50 kg myI = ⋅
Kinetic energy. 2 2 2 21 1 1 1
2 2 2 2x x y y z zT mv I I Iω ω ω= + + +
xy x y yz y z xz x zI I Iω ω ω ω ω ω− − −
( )( )210 1.50 6 0 0 0 0 0
2T = + + + + + +
27.0 JT = !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 50.
From the solution given in the textbook for Sample Prob. 18.1,
2 21 1, ,
12 12x yI mb I ma= =
Initial state: = 0, 0 0Τ1= , =v ωωωω
Final state: =F t
m
∆ −
v k
( )6F ta b
mab
∆ = −
i jωωωω
or 0, 0,x y zF t
v v vm
∆= = = −
6
, 6 , 0x y zF t
F tmb
ω ω ω∆= = − ∆ =
Additional moments and products of inertia.
( )2 21, 0
12z xy yz zxI m a b I I I= + = = =
Final kinetic energy.
2 2 2 22
1 1 1 1
2 2 2 2x x y y z zT mv I I Iω ω ω= + + +
2 2 2
2 21 1 1 6 1 1 60
2 2 12 2 12
F t F t F tm mb ma
m mb ma
∆ ∆ ∆ = + + +
( ) ( ) ( ) ( )2 2 2 2
1 3 3 7
2 2 2 2
F t F t F t F t
m m m m
∆ ∆ ∆ ∆= + + =
Kinetic energy imparted. 2 1T T T∆ = −
( )27
2
F tT
m
∆∆ = !
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Chapter 18, Solution 51.
Point of impact: ( ) ( )2.7 m 0.225 mA = +r i k
Initial linear momentum of the meteorite, ( )kg m/s :⋅
( )( )0 0.14 720 900 960 100.8 126 134.4m = − + = − +v i j k i j k
Its moment about the origin, ( )2kg m /s :⋅
0 2.7 0 0.225 28.35 340.2 340.2
100.8 126 134.4A m× = = − −
−
i j k
r v i j k
Final linear momentum of meteorite and its moment about the origin, ( ) ( )2kg m/s and kg m /s .⋅ ⋅
00.8 80.64 100.8 107.5m = − +v i j k
( )00.8 22.68 272.16 272.16A m× = − −r v i j k
Let AH be the angular momentum of the probe and m′ be its mass. Conservation of angular momentum about the origin for a system of particles consisting of the probe plus the meteorite:
( )0 00.8A A Am m× = + ×r v H r v
( ) ( ) ( )2 2 25.67 kg m /s 68.04 kg m /s 68.04 kg m /s ,A = ⋅ − ⋅ − ⋅H i j k
( ) ( )( )( )2 2
5.67, 0.012496 rad/s
1500 0.55
A xx x A xx
x
HI H
m kω ω= = = =
′
( )( )
( )( )2 2
68.04, 0.139612 rad/s
1500 0.57
A yy y A yy
y
HI H
m kω ω −= = = = −
′
( ) ( )( )( )2 2
68.04, 0.18144 rad/s
1500 0.50
A zz z A zz
z
HI H
m kω ω −= = = = −
′
Kinetic energy of motion of the probe about its mass center:
( ) ( )2 2 2 2 2 2 2 2 21
2 2x x y y z z x x y y z zm
T I I I k k kω ω ω ω ω ω= + + = + +
( ) ( ) ( ) ( ) ( ) ( )2 2 2 2 2 215000.55 0.012496 0.57 0.139612 0.50 0.18144
2 = + +
2 210.96 kg m /s 10.96 N m= ⋅ = ⋅ 10.96 JT = !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 52.
Point of impact: ( ) ( )2.7 m 0.225 mA = +r i k
Initial linear momentum of the meteorite, ( )kg m/s :⋅
( )( )0 0.14 0.14 0.14 0.14x y z x y zm v v v v v v= + + = + +v i j k i j k
Its moment about the origin, ( )2kg m /s :⋅
( ) 002.7 0 0.225
0.14 0.14 0.14A A
x y z
m
v v v
= = =i j k
H r v
( )0.0315 0.378 0.0315 0.378y z x yv v v v= − − − +i j k
Final linear momentum of the meteorite, ( )kg m/s :⋅
00.75 0.105 0.105 0.105x y zm v v v= + +v i j k
Its moment about the origin, ( )2kg m /s :⋅
( ) ( )00.75 0.023625 0.2835 0.023625 0.2835A y z x ym v v v v× = − − − +r v i j k
Initial linear momentum of the space probe, ( )kg m/s :⋅ 0 0m′ ′ =v
Final linear momentum of the space probe, ( )kg m/s :⋅
( ) ( )1500 0.017x y z y zm v v v v v′ ′ ′ ′ ′ ′+ + = − + +i j k i j k
Final angular momentum of space probe, ( )2kg m /s :⋅
( )2 2 2A x x y y z zH m k k kω ω ω′= + +i j k
( ) ( ) ( ) ( ) ( )2 2 21500 0.55 0.05 0.57 0.12 0.50 zω = + − +
i j k
22.6875 58.482 375 zω= − +i j k
Conservation of linear momentum of the probe plus the meteorite, ( )2kg m /s :⋅
0.14 0.14 0.14 0.105 0.105 0.105x y z x y zv v v v v v+ + = + +i j k i j k
( ) ( )1500 0.017 1500 1500y zv v′ ′+ − + +i j k
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: 0.035 25.5xv = −i 728.57 m/sxv = −
: 0.035 1500y yv v′=j
: 0.035 1500z zv v′=k
Conservation of angular momentum about the origin.
( ) ( )0.0315 0.378 0.0315 0.378 0.023625 0.2835 0.023625y z x y y z xv v v v v v v− − − + = − − −i j k i j
0.2835 22.6875 58.482 375y zv ω+ + − +k i j k
: 0.007875 22.6875yv− =i 2880.95 m/syv = −
: 0.0945 375y zv ω− =k
6252 10z yvω −= − × 0.726 rad/szω = −
Kinetic energy of motion of probe relative to its mass center:
( ) ( )2 2 2 2 2 2 2 2 21 1
2 2x x y y z z x x y y z zT I I I m k k kω ω ω ω ω ω′ = + + = + +
( ) ( ) ( ) ( ) ( ) ( ) ( )2 2 2 2 2 211500 0.55 0.05 0.57 0.12 0.50 0.726
2 = + − + −
102.9 JT ′ = !
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Chapter 18, Solution 53.
The disk is constrainted to rotate about the fixed point A. Point B of the disk does not rebound after the impact. ( ) 0B zv =
Kinematics. /B B A= ×v rω
( ) ( )0
B B x y zx zv va a
ω ω ω+ =−
i j ki k
( ) ,B zxv aω= − ( ) ,B zyv aω= 0 x ya aω ω= − − 0x yω ω+ = (1)
Moments of inertia: 2 2 21 5 ,4 4xI ma ma ma= + = 21 ,
4yI ma= 2 2 21 32 2zI ma ma ma= + =
Impulse-Momentum Principle:
Moments about A: ( ) ( ) ( ) ( )0 1A Aa a B t+ − × ∆ =H i j k H
( ) ( )0y x x y y z zI aB t a B t I I Iω ω ω ω+ − ∆ − ∆ = + +j i j i j k
Substitute values for , ,x yI I and zI and resolve into components.
( ) 25: 04 xaB t ma ω− ∆ =i (2)
( )2 20
1 1: 4 4 yma aB t maω ω− ∆ =j (3)
21: 02 zma ω=k 0zω =
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Solving (1), (2) and (3) simultaneously for , x yω ω and B t∆
01 ,6xω ω= − 0
1 ,6yω ω= 0
524
B t maω∆ =
Angular velocity: 0 01 16 6
ω ω ω= − +i j
Kinetic energy before impact: 2 2 20 0 0
1 12 8yT I maω ω= =
Kinetic energy after impact: 2 2 21
1 1 12 2 2x x y z zT I I Iω ω ω= + +
2 22 2 2 2
1 0 0 01 5 1 1 1 1 102 4 6 2 4 6 48
T ma ma maω ω ω = − + + =
Energy lost: 2 20 1 0
548
T T ma ω− = 2 20
548
ma ω "
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 54.
Principle of impulse-momentum:
Linear momentum: ( )0 x y zmv C t mv mv mv− + ∆ = + +j j i j k
: 0 xmv=i 0xv =
0: ymv C t mv− + ∆ =j ( )0 yC t m v v∆ = + (1)
: 0 zmv=k 0zv =
Since impact is perfectly plastic, ( ) 0.C yv =
( ) ( )/C G C G y x y zr v a cω ω ω= + × = + + + × −v v j i j k i kωωωω
( ) ( ) ( )C C y y x z yx zv v c v c a aω ω ω ω+ = − + + + −i k i j k
: 0C x zv c aω ω+ + =j y x zv c aω ω= − −
Moments about C:
( ) ( ) ( ) ( )0 0 G G G yx y zcmv amv H H a c mv+ = + + + − + ×i k H i j k i k j
( )2 2 2 22 2 2
3 3 3x y z y ymc m c a ma mcv mavω ω ω= + + + − −i j k i k
20
1:
3 x ycmv mc mcvω= −i (3)
( )2 21: 0
3 ym c a ω= +j 0yω =
20
1:
3 z yamv ma mavω= −k (4)
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After using (2) to eliminate ,yv (3) and (4) become
04
3 x zc a vω ω+ =
04
3x zc a vω ω+ =
from which 03
,7xc vω = 0
3
7za vω =
From (2), 0 0 03 3 6
7 7 7yv v v v= − − = −
Kinetic energy before impact: 20 0
1
2T mv=
Kinetic energy after impact: 2 2 2 21
1 1 1 1
2 2 2 2x x y y z zT mv I I Iω ω ω= + + +
22 2 2 2
1 01 6 1 1 1 1
02 7 2 3 2 3x zT m v mc maω ω = + + +
2 2 2
20 0 0 0
1 6 1 3 1 3 3
2 7 3 7 3 7 7m v v v mv = + + =
Energy lost: 20 1 0
1
14T T mv− = 2
0 1 01
14T T mv− = !
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Chapter 18, Solution 55.
From the solution to Prob. 18.1
( ) ( )2 21.296 kg m /s 0.702 kg m /sG = ⋅ − ⋅H i k
( )10 rad/s= iωωωω
Let the frame of reference , ,x y z′ ′ ′ be rotating with angular velocity.
( )10 rad/s= iΩΩΩΩ
Rate of change ofG GH H& .
( )G G GGx y z′ ′ ′= + ×H H H& & ΩΩΩΩ
( )0 10 1.296 0.702 7.02= + × − =i i k j
( )7.02 N mG = ⋅H j& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 56.
Use principal axes , y z′ ′ as shown.
cos 45 , sin 45y zω ω ω ω′ ′= ° = °
0xω ′ =
2 21 1,
3 12x yI ma I ma′ ′= =
25
12z x yI I I ma′ ′ ′= + =
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +H i j k
( ) ( )2 21 50 cos 45 sin 45
12 12ma maω ω ′ ′= + ° + °
j k
( ) ( )21cos 45 cos 45 sin 45
12A ma ω = ° ° − °
H j k
( ) ( )25sin 45 sin 45 cos 45
12ma ω + ° ° + °
j k
( )2
3 212
ω= +H j kAma
Let the frame of reference Axyz be rotating with angular velocity
ω= jΩΩΩΩ
Then, ( )A AAxyz= + ×H H Η& & ΩΩΩΩ
( )2 2 2
0 3 212 6
ma maω ωω= + × + =j j k i
2 216A ma ω=H i& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 57.
23.60.1118 lb s /ft 24 in. 2 ft
32.2m l= = ⋅ = =
( ) ( )1200 2125.664 rad/s
60
πω = =
Use principal axes , x y′ ′ as shown.
sin 20 42.980 rad/sxω ω′ = − ° = −
cos 20 118.085 rad/syω ω′ = ° =
For the rod, 0xI ′ ≈
( ) ( )22 21 10.1118 2 0.037267 lb s ft
12 12yI ml′ = = = ⋅ ⋅
G x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +′ ′ ′H i j k
( ) ( )0 0.037267 118.085 0= + +′j
4.40068= ′j
( )4.40068 sin20 cos 20= ° + °i j
( ) ( )1.5051 lb s ft 4.1353 lb s ft= ⋅ ⋅ + ⋅ ⋅i j
Let the frame of reference Gxyz be rotating with angular velocity
( )125.664 rad/sω= j jΩ =Ω =Ω =Ω =
Then, ( )G G GGxyz= + ×H H Η& & ΩΩΩΩ
( ) ( ) ( )0 125.664 1.5051 4.1353 189.14 lb ftG = + × + = − ⋅H j i j k&
( )189.1 lb ftG = − ⋅H k& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 58.
Use principal axes , , x y z′ ′ ′ as shown.
cos sinβ β= +′i i j
sin cosβ β= − +′j i j
cos sinβ β= −′ ′i i j
sin cosβ β= +′ ′j i j
( ) ( )cos sinω ω β ω β= = −′ ′i i jωωωω
( ) ( )cos sin 0ω ω β ω β= = − =′ ′i i j& & &αααα
Principal moments of inertia:
2 21 1,
2 4x y zI mr I I mr′ ′ ′= = =
Angular momentum:
G x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +′ ′ ′H i j k
2 21 1cos sin
2 4mr mrω β ω β= −′ ′i j
Let the frame of reference Gx y z′ ′ ′ be rotating with angular velocity
ω=ΩΩΩΩ
( ) 0G G G GGx y z′ ′ ′= + × = + ×H H Η H& & Ω ΩΩ ΩΩ ΩΩ Ω
( ) 2 21 1cos sin cos sin
2 4mr mrω β ω β ω β β = − × −′ ′ ′ ′
i j i j
2 21sin cos
4mr ω β β= k
2 21sin cos
4G mr ω β β=H k& !
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Chapter 18, Solution 59.
( ) ( )2 1 4 rad/s 12 rad/sω ω= + = +j k j kωωωω
For axes , , x y z′ ′ ′ parallel to x, y, z with origin at A,
( ) ( )22 21 18 0.100 0.02 kg m
4 4xI mr′ = = = ⋅
2 20.02 kg m , 0.04 kg my x z x yI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′= + +H i j k
( )( ) ( )( ) ( ) ( )2 20 0.02 4 0.04 12 0.08 kg m /s 0.48 kg m /s= + + = ⋅ + ⋅j k j k
Let the frame of reference Axyz be rotating with angular velocity
( )2 4 rad/sω= =j jΩΩΩΩ
Then, ( ) 20A A A AAxyzω= + × = + ×H H Η j Η& & ΩΩΩΩ
( ) ( )2 24 0.08 0.48 1.92 kg m /sA = × + = ⋅H j j k i&
( )1.920 N mA = ⋅H i& !
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Chapter 18, Solution 60.
( ) ( )2 1 8 rad/s 16 rad/sω ω= + = +i j i jωωωω
For axes , , x y z′ ′ ′ parallel to x, y, z with origin at A,
( ) ( )22 21 16 0.160 0.0384 kg m
4 4xI mr′ = = = ⋅
2 20.0384 kg m , 0.0768 kg mz x y x zI I I I I′ ′ ′ ′ ′= = ⋅ = + = ⋅
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′= + +H i j k
( ) ( ) ( ) ( )0.0384 8 0.0768 16 0= + +i j
( ) ( )2 20.3072 kg m /s 1.2288 kg m /s= ⋅ + ⋅i j
Let the frame of reference Axyz be rotating with angular velocity
( )2 8 rad/sω= =i iΩΩΩΩ
Then, ( ) 0A A A AAxyzω= + × = + ×H H Η i Η& &
2222ΩΩΩΩ
( ) ( )2 28 0.3072 1.2288 9.8304 kg m /sA = × + = ⋅H i i j k&
( )9.83 N mA = ⋅H k& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 61.
Use principal axes , y z′ ′ as shown.
cos 45 , sin 45y zω ω ω ω′ ′= ° = °
0xω ′ =
2 21 1,
3 12x yI ma I ma′ ′= =
25
12z x yI I I ma′ ′ ′= + =
A x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +H i j k
( ) ( )2 21 50 cos 45 sin 45
12 12ma maω ω ′ ′= + ° + °
j k
( )( )21cos 45 cos 45 sin 45
12A ma ω = ° ° − °
H j k
( )( )25sin 45 sin 45 cos 45
12ma ω + ° ° + °
j k
( )2
3 212
ω= +H j kAma
Let the frame Axyz be rotating with angular velocity .ω=Ω j
Then ( )A A AAxyzH= + ×H Ω H& &
where ( ) ( ) ( )2 2
3 2 3 212 12A Axyz
ma maH
ω α= + = +j k j k&&
and ( )2 2 2
3 212 6A
ma maω ωω
× = × + =
Ω H j j k i
So ( )2
22 3 212A
ma ω α α= + +H i j k& "
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Chapter 18, Solution 62.
Use principal axes , ,x y z′ ′ ′ as shown.
cos sinβ β′ = +i i j
sin cosβ β′ = − +j i j
cos sinβ β′ ′= −i i j
sin cosβ β′ ′= +j i j
( ) ( )cos sinω ω β ω β′ ′= = −ω i i j
( ) ( )cos sinα α β α β′ ′= = −α i i j
Principal moments of inertia:
2 21 1,2 4x y zI mr I I mr′ ′ ′= = =
Angular momentum:
G x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′= + +H i j k
2 21 1cos sin2 4
mr mrω β ω β= −i j
Let the frame of reference Gx y z′ ′ ′ be rotating with angular velocity
ω=Ω
( )G G GGx y z′ ′ ′= + ×H H H! ! Ω
x x y y z zI I Iα α α′ ′ ′ ′ ′ ′′ ′= + +i j k
( ) 2 21 1cos sin cos sin2 4
mr mrω β ω β ω β β ′ ′ ′ ′+ − × −
i j i j
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( )( )21 cos cos sin2
mr α β β β = +
i j
( )( )21 sin sin cos 04
α β β β + − − + +
mr i j
2 21 sin cos4
mr ω β β+ k
( )2 2 21 2cos sin4G mr α β β= +H i! 2 2 21 1sin cos sin cos
4 4mr mrα β β ω β β+ +j k !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 63.
Mass of sheet metal: 1.5 kg.=m
Sheet metal dimension: 0.120 m=b
Area of sheet metal: 2 2 2 2 2 21 1 3 0.0432 m2 2
= + + + = =A b b b b b
Let
21.5 34.722 kg/m mass per unit area.0.0432
ρ = = = =mA
Moments and products of inertia: mass areaρ=I I
xy plane (rectangles)
4 4 41 1 23 3 3
= + =xI b b b
( )( )442 2 34.722 0.1203 3
ρ= =xI b
3 24.8 10 kg m−= × ⋅
( ) ( )2 2 43 1 5 1 12 2 2 2 2
= + − = −
xyI b b b b b b b
( )( )441 1 34.722 0.1202 2xyI bρ= − = −
3 23.6 10 kg m−= − × ⋅
xz plane (triangles)
4 4 41 1 112 12 6
= + =xI b b b
( )( )441 1 34.722 0.1206 6
ρ= =xI b
3 21.2 10 kg m−= × ⋅
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
For calculation of ,xzI use pairs of elements 1dA and 2 :dA 2 1.=dA dA
( ) ( ) ( ) 21 2 1 04 2 2
2 2 = + − − = − − = − −
∫ ∫ ∫ ∫b
xzz zI x dA b x dA b x zdA b x z dx
but .z x=
Hence, ( )2 3 4 4 40
2 1 523 4 12
= − − = − − = −
∫a
xzI bx x dx b b b
( )( )44 3 25 5 34.722 0.120 3.0 10 kg m12 12
ρ −= − = − = − × ⋅xzI b
Total for :xI 3 3 3 24.8 10 1.2 10 6.0 10 kg m− − −= × + × = × ⋅xI
The mass center lies on the rotation axis, therefore 0=a
0 mΣ = + = = = −F A B a A B
, A x xy xzI I Iω ω ω ω α= − − = =H i j k i iω α
Let the frame of reference Axyz be rotating with angular velocity
ω= = iΩ ω
( )A A A AAxyzΣ = = + ×M H H H! ! Ω
( ) ( )0 4 α α α ω ω ω ω+ × + = − − + × − −y z x xy xz x xy xzM b B B I I I I I Ii i j k i j k i i j k
( ) ( )2 20 4 4 α α ω α ω− + = − − − +z y x xy xz xz xyM bB bB I I I I Ii j k i j k
Resolve into components and solve for yB and .zB
0: xM I α=i
( )2
: 4
xy xzz
I IB
b
α ω−=j
( )2
: 4
xz xyy
I IB
b
α ω+= −k
Data: ( )0
2 2400, 25.133 rad/s, 0.120 m 0
60π
α ω= = = = =b M
( )( )( )( )
230 3.0 10 25.1333.95 N
4 0.120
−− − ×= =zB
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( )( )
( )( )
230 3.6 10 25.1334.74 N
4 0.120
−+ − ×= − =yB
4.74 N= − = −y yA B
3.95 N= − = −z zA B
( ) ( )4.74 N 3.95 N= − −A j k !
( ) ( )4.74 N 3.95 N= +B j k !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 64.
Mass of sheet metal: 1.5 kg.=m
Sheet metal dimension: 0.120 m=b
Area of sheet metal: 2 2 2 2 2 21 13 0.0432 m
2 2= + + + = =A b b b b b
Let
21.534.722 kg/m mass per unit area.
0.0432ρ = = = =m
A
Moments and products of inertia: mass areaρ=I I
xy plane (rectangles)
4 4 41 1 2
3 3 3= + =xI b b b
( )( )442 234.722 0.120
3 3ρ= =xI b
3 24.8 10 kg m−= × ⋅
( ) ( )2 2 43 1 5 1 1
2 2 2 2 2 = + − = −
xyI b b b b b b b
( )( )441 134.722 0.120
2 2xyI bρ= − = −
3 23.6 10 kg m−= − × ⋅
xz plane (triangles)
4 4 41 1 1
12 12 6= + =xI b b b
( )( )441 134.722 0.120
6 6ρ= =xI b
3 21.2 10 kg m−= × ⋅
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For calculation of ,xzI use pairs of elements 1dA and 2 :dA 2 1 =dA dA
( ) ( ) ( ) 21 2 1 0
4 2 22 2
= + − − = − − = − −
∫ ∫ ∫ ∫b
xzz z
I x dA b x dA b x zdA b x z dx
But ,=z x
Hence, ( )2 3 4 4 40
2 1 52
3 4 12 = − − = − − = −
∫a
xzI bx x dx b b b
( )( )44 3 25 534.722 0.120 3.0 10 kg m
12 12ρ −= − = − = − × ⋅xzI b
Total for :xI 3 3 3 24.8 10 1.2 10 6.0 10 kg m− − −= × + × = × ⋅xI
The mass center lies on the rotation axis, therefore 0=a
0 Σ = + = = = −F mA B a A B
, ω ω ω ω α= − − = =A x xy xzI I IH i j k i iω αω αω αω α
Let the frame of reference Axyz be rotating with angular velocity
ω= = iΩ ωΩ ωΩ ωΩ ω
( )A A A AAxyzΣ = = + ×M H H H& & ΩΩΩΩ
( ) ( )0 4 α α α ω ω ω ω+ × + = − − + × − −y z x xy xz x xy xzM b B B I I I I I Ii i j k i j k i i j k
( ) ( )2 20 4 4 α α ω α ω− + = − − − +z y x xy xz xz xyM bB bB I I I I Ii j k j k
Resolve into components and solve for yB and ,zB
0: xM I α=i
( )2
: 4
xy xzz
I IB
b
α ω−=j
( )2
: 4
xz xyy
I IB
b
α ω+= −k
Data: ( )2 360
0, 37.699 rad/s60
πα ω= = =
0 0=M
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( ) ( )
( )( )
230 3.0 10 37.6998.88 N
4 0.120
− − − × = =zB
( ) ( )( )( )
230 3.6 10 37.69910.66 N
4 120
− + − × = − =yB
10.66 N= − = −y yA B
8.88 N= − = −z zA B
( ) ( )10.66 N 8.88 N= − −A j k"
( ) ( )10.66 N 8.88 N= +B j k"
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 65.
Use principal axes x′, y′, z′ as shown.
( ) ( )cos sinω θ ω θ′ ′= −i jωωωω
0=αααα Moments of inertia:
2 21 1,
2 4′ ′ ′= = =x y zI mr I I mr
Angular momentum:
ω ω ω′ ′ ′ ′ ′ ′′= + +&G x x y y z zI I IH i j k
2 21 1cos sin
2 4ω θ ω θ= −mr mri j
Let the frame of reference Gx′y′z′ be rotating with angular velocity =Ω ωΩ ωΩ ωΩ ω
( ) ′ ′ ′= + ×& &
G G GGx y zH H HΩΩΩΩ
( ) 2 21 1cos sin cos sin
2 4x x y y z zI I I mr mrα α α ω θ ω θ ω θ θ′ ′ ′ ′ ′ ′ ′ ′ ′ ′ ′ ′= + + + − × −
i j k i j i j
2 21sin cos
4ω θ θ= mr k
Since the mass center G lies on the rotation axis, 0, 0= =v a
: 0 m mΣ = + = = = −F a A B a B A
( ): 2G G y zM a a a A AΣ = − × + × = − × +H i A i B i j k&
2 212 2 sin cos
4ω θ θ− =z yaA aA mrj k k
( )
( )
22
2 2
8 1010 sin 20 cos 20
32.2 121 sin cos0.4159 lb
8 208
12
ymr
Aa
ω θ θ
° ° = − = − = −
0=zA ( )0.416 lb= −A j""""
0.4159 lb, 0yy zB A B= − = = ( )0.416 lb=B j""""
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 66.
Length of rod: 8 8
2.76106 ft12 12
L π= + =
Angular velocity: ( )20 rad/sω= =i iωωωω
Angular acceleration: α= iαααα
Angular momentum: ω ω= −G x xzI IH i k
Let the reference frame Gxyz be rotating with angular velocity
ω= = iΩ ωΩ ωΩ ωΩ ω
Rate of change of angular momentum: ( )= + ×& &G G GGxyz
H H HΩΩΩΩ
( )G x x xz x x xzI I I Iα α ω ω ω= − + × −H i k i i k&
2x xz xzI I Iα ω α= + −i j k
Since the mass center G lies on the rotation axis, 0, 0 8 in. + 4 in. = 1 ftb= = =v a
: m mΣ = + = = −F a A B a B A
( ) ( )0 0 2Σ = + − × + × = − ×G M b b M bM i i A i B i i A
( ) ( )0 02 2 2= − × + = + −y z z yM b A A M bA bAi i j k i j k
Set Σ = &G GM H and resolve into components.
0: xM I α=i
22: 2
2xz
z xz z zI
bA I A Bb
ωω= = = −j
: 2 2xz
y xz y yI
bA I A Bb
αα− = − = = −k
Calculation of xI and xzI :
Let mass per unit length .ρ = = m
L
For portions AC and DB,
0, 0= =x xzI I
For portion CG use polar coordinate .θ
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( )1 cos , sin θ θ ρ θ= − − = − =x r z r dm rd
2 2 2 30
sin2
π πθρ θ ρ= = =∫ ∫xI z dm r rd r
( )2 30
1 cos sin 2π θ θρ θ ρ= = − =∫ ∫xzI xzdm r rd r
Likewise, for portion GD, 3 3, 22
π ρ ρ= =x xzI r I r
Total: 3 3
3 3 4, 4
ππρ ρ= = = =x xzmr mr
I r I rL L
Data: 21.6 40.049689 lb s /ft 4 in. ft
32.2 12
Wm r =
g= = = ⋅ =
( )
3
2
40.049689
12 0.0020940 lb s ft2.76106xI
π = = ⋅ ⋅
( )( )
3
2
44 0.049689
12 0.0026661 lb s ft2.76106xzI
= = ⋅ ⋅
Reactions: Since 0M is zero, 0α = .
( )( )
( )( )2
0.0026661 200.53322
2 1z zA B= = = −
0y yA B= = − ( )0.533 lb=A k "
( )0.533 lb= −B k "
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 67.
The mass center G lies on fixed axis of rotation so that 0.=a
Resultant force on assembly: = 0mΣ =F a
0+ =A B = −A B
Angular velocity: ( )20 rad/s=ω k
20 rad/s, 0z x yω ω ω= = =
Angular momentum about .G
G xz yz zI I Iω ω ω= − − +H i j k
Rate of change of .GH Let the reference frame Gxyz be rotating with angular velocity ( )20 rad/s= =Ω ω k
( ) 0G G G GGxyz= + × = + ×H H Ω H ω H& &
( )xz yz zI I Iω ω ω ω= × − − −k i j k
2 2yz xzI Iω ω= −i j
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Calculation of products of inertia yzI and xzI
( )( )( ) ( )( )( ) 21 1 1 2 2 2 2.4 0.100 0.100 2.4 0.100 0.100 0.048 kg myzI m y z m y z= + = + − = ⋅
( )( )( ) ( )( )( ) 21 1 1 2 2 2 2.4 0.100 0.100 2.4 0.100 0.100 0.048 kg mxzI m x z m x z= + = − + − = − ⋅
Couple formed by reactions A and B.
( )/ 0.600 0.6 0.6B A x y y xB B B B= × = − × + = −M r B k i j i j
G=M H& Resolve into components.
( )( )22: 0.6 0.048 20 19.2y yzB I ω= = =i
( )( )22: 0.6 0.048 20 19.2x xzB I ω− = − = − − =j
32 N, 32 N, 32 N, 32 Nx y x yB B A A= − = = = −
Dynamic reactions. ( ) ( )32.0 N 32.0 N= −A i j "
( ) ( )32.0 N 32.0 N= − +B i j"
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 68.
By symmetry, the mass center is at G as shown. Angular velocity and angular acceleration: , ω α ω= = = !j j jω α
Angular momentum about the mass center: ω ω ω= − + −G xy y yzI I IH i j k
Since the body lies in the xy plane, 0.=yzI
Let the reference frame Gxyz be rotating with angular velocity ω= jΩ
( ) ( )ω ω ω ω ω= + × = − + + × − +! ! ! !G G G xy y xy yGxyzI I I IH H H i j j i jΩ
2α α ω= − + +xy y xyI I Ii j k
Calculation of xyI and :yI Let 2 mass per unit area.ρ = = =m mA ab
( ) ( )mass area.ρ=I I
For the pairs of area elements shown,
2el el2 2
2= = =xy
xdI x y dA yxdy x ydy
2
20 0a a
xybyI x ydy b ydya
= = −
∫ ∫
2 2
2 2 320 0 02a a ab bb ydy y dy y dy
a a= − +∫ ∫ ∫
2 2 2 3 2 2 2 21 2 1 12 3 4 12
= − + =b a b a b a b a
3 31 1212 6 = =
yI ab ab
For mass, 21 1, 6 3
= =xy yI mab I mb
Since the mass center lies on the rotation axis, 0.=a
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effΣ = ΣF F
0+ = =mA B a
= −B A
Reactions A and B form a couple.
Σ = !G GM H
( )0 + × + = !x z GM c A Aj j i k H
0+ − = !z x GcA M cAi j k H
Resolve into components.
: xyz xy z
IcA I A
cα
α= − = −i (1)
0: yM I α=j (2)
2
2: xyx xy x
IcA I A
cω
ω− = = −k (3)
Data: 5 kg, 900 mm 0.9 m, 600 mm 0.6 m, 2 1.8 m= = = = = = =m a b c a
8 rad/s, 0ω α= =
( )( ) ( )( )( )2 2 21 15 0.6 0.60 kg m , 5 0.9 0.6 0.45 kg m3 6
= = ⋅ = = ⋅y xyI I
From (2), 0 0=M
From (3), ( )( )20.45 816 N
1.8xA = − = −
From (1), 0=zA ( )16.00 N= −A i !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 69.
By symmetry, the mass center is at G as shown.
Angular velocity and angular acceleration: , ω α ω= = = &j j jω αω αω αω α
Angular momentum about the mass center: ω ω ω= − + −G xy y yzI I IH i j k
Since the body lies in the xy plane, 0.=yzI
Let the reference frame Gxyz be rotating with angular velocity ω= jΩΩΩΩ
( ) ( )ω ω ω ω ω= + × = − + + × − +& & & &G G G xy y xy yGxyzI I I IH H H i j j i jΩΩΩΩ
2α α ω= − + +xy y xyI I Ii j k v
Calculation of xyI and :yI Let 2
mass per unit area.ρ = = =m m
A a
( ) ( )mass area.ρ=I I
For the pairs of area elements shown,
2el el2 2
2= = =xy
xdI x y dA yxdy x ydy
2
20 0
a axy
byI x ydy b ydy
a = = −
∫ ∫
2 2
2 2 320 0 0
2a a ab bb ydy y dy y dy
a a= − +∫ ∫ ∫
2 2 2 3 2 2 2 21 2 1 1
2 3 4 12= − + =b a b a b a b a
3 31 12
12 6 = =
yI ab ab
For mass, 21 1,
6 3= =xy yI mab I mb
Since the mass center lies on the rotation axis, 0.=a
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effΣ = ΣF F
0+ = =mA B a
= −B A Reactions A and B form a couple.
Σ = &G GM H
( )0 + × + = &x z GM c A Aj j i k H
0+ − = &z x GcA M cAi j k H
Resolve into components.
: xyz xy z
IcA I A
c
αα= − = −i (1)
00: y
y
MM I
Iα α= =j (2)
2
2: xyx xy x
IcA I A
c
ωω− = = −k (3)
Data: 5 kg, 900 mm 0.9 m, 600 mm 0.6 m, 2 1.8 m= = = = = = =m a b c a
00, 36 N mω = = ⋅M
( )( ) ( )( )( )2 2 21 15 0.6 0.60 kg m , 5 0.9 0.6 0.45 kg m
3 6= = ⋅ = = ⋅y xyI I
(a) From (2), 23660 rad/s
0.60α = = 260.0 rad/sα = "
From (3), 0=xA
(b) From (1), ( )( )0.45 60
15.00 N1.8
= − = −zA ( )15.00 N= −A k"
( )15.00 N=B k"
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 70.
The sheet metal component rotates about the fixed z axis, so that equations (18.29) of the textbook apply. These are relisted below as equations (1), (2), and (3).
2x xz yzM I Iα ωΣ = − + (1)
2y yz xzM I Iα ωΣ = − − (2)
z zM I αΣ = (3)
Calculation of the required moment and products of inertia. Total mass: 600 g 0.6 kgm = =
Total area: ( ) ( )( ) ( )2 2 3 21 10.075 0.150 0.075 0.075 16.875 10 m2 2
A −= + + = ×
Let ρ be the mass per unit area. 235.556 kg/mmA
ρ = =
The component is comprised of 3 parts: triangle 1, triangle 2, and rectangle 3 as shown. Let the lengths of 75 mm be labeled b. Triangle 1. The equation of the upper edge is
2by z= −
Use elements of width dz and height y.
( ) 2el
112zdm ydz dI y dmρ= =
( ) ( )el el0 0xz yzdI dI= =
Coordinates of the element mass center:
el el el1, ,2
x b y y z z= − = =
( ) el elelxz xzdI dI x z dm= +
( ) ( )02zbb z yd bz z dzρ ρ = + − = − −
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42
2
12 12
b
xz bbI b z z dz bρ ρ
−
= − − =
∫
( ) el elelyz yzdI dI y z dm= +
( )21 10
2 2 2by z ydz z zdzρ ρ = + = −
2
42
2
1 12 2 24
b
yz bbI z zdz bρ ρ
−
= − = −
∫
( ) ( )2 2el elelz zdI dI x y dm= + +
2 2 2 2 31 1 112 4 3
y b y ydz b y y dzρ ρ = + + = +
3 2 2 313 5 1 124 4 2 3
b b z bz z dzρ = − + −
3 2 2 3 42
2
13 3 1 1 724 4 2 3 12
b
z bI b b z bz z dz bρ ρ−
= − + − =
∫
Applying the data,
( )( )4 6 21 35.556 0.075 93.75 10 kg m12xzI −= = × ⋅
( )( )4 6 21 35.556 0.075 46.875 10 kg m24yzI −= − = − × ⋅
( )( )4 6 27 35.556 0.075 656.25 10 kg m12zI −= = × ⋅
Triangle 2. The equation of the lower edge is .2by z = − −
Use elements of width dz and height y.
( ) ( ) ( )2el el el
1, , 0, 012z zx yzdm ydz dI y dm dI dIρ= − = = =
Coordinates of the element mass center:
el el el1, ,2
x b y y z z= = =
The integrals for , ,xz yzI I and zI turn out to be the same as those of triangle 1.
6 2 6 2 6 293.75 10 kg m , 46.875 10 kg m , 656.25 10 kg mxz yz zI I I− − −= × ⋅ = − × ⋅ = × ⋅
continued
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Rectangle 3. Area: ( )( ) 3 20.150 0.075 11.25 10 mA −= = ×
Mass: 3400 10 kgm Aρ −= = ×
0, 0xz yzI I= =
( ) ( )( )2 23 6 21 12 400 10 0.150 750 10 kg m12 12zI m b − −= = × = × ⋅
Totals. 6 2187.5 10 kg mxz xzI I −= Σ = × ⋅
6 293.75 10 kg myz yzI I −= Σ = − × ⋅
6 22062.5 10 kg mz zI I −= Σ = × ⋅
Since the mass center lies on the fixed axis, the acceleration a of the mass center is zero.
0mΣ = =F a
The reactions at A and B form a couple.
= −B A
Let x yA A= +A i j
Resultant couple acting on the body:
( ) 0x yc A A M= × + +M k i j k
0y xcA cA M= − + +i j k
(a) Moment 0.M Using equation (3),
( )( )60 2062.5 10 12z zM M I α −Σ = = = ×
30 24.8 10 N mM −= × ⋅ !
(b) Reactions at A and B for the case 0.ω =
2x y xz yz xzM cA I I Iα ω αΣ = − = − − = −
( )( )6
3187.5 10 12
15 10 N0.150
xzy
IAcα
−−
×= = = ×
2y x yz xz yzM cA I I Iα ω αΣ = = − − = −
( )( )6
393.75 10 12
7.5 10 N0.150
yzx
IA
cα −
−− ×
= − = − = ×
( ) ( )3 37.50 10 N 15.00 10 N− −= × + ×A i j !
( ) ( )3 37.50 10 N 15.00 10 N− −= − × − ×B i j !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 71.
Use principal axes x′, y′, z′ as shown.
0=ωωωω
( ) ( )cos sinα θ α θ′ ′= −i jαααα
Moments of inertia:
2 21 1,
2 4′ ′ ′= = =x y zI mr I I mr
Angular momentum:
ω ω ω′ ′ ′ ′ ′ ′′= + +&G x x y y z zI I IH i j k
2 21 1cos sin
2 4ω θ ω θ= −mr mri j
Let the frame of reference Gx′y′z′ be rotating with angular velocity
= =Ω ω 0Ω ω 0Ω ω 0Ω ω 0
( ) ′ ′ ′= + ×& &
G G GGx y zH H HΩΩΩΩ
0α α α′ ′ ′ ′ ′ ′′ ′= + + +x x y y z zI I Ii j k
2 21 1cos sin
2 4α θ α θ′ ′= −mr mri j
( ) ( )2 21 1cos cos sin sin sin cos
2 4α θ θ θ α θ θ θ= + − − +mr mri j i j
2 2 2 21 1 1cos sin sin cos
2 4 4α θ θ α θ θ = + +
mr mri j
Since the mass center G lies on the rotation axis, 0, 0= =v a
: 0 m mΣ = + = = = −F a A B a B A
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( ) ( ) ( ) ( )0Σ = + − × + + × +G y z y zM a A A a B BM i i j k i j k
( )0 02 2 2y z z yM a A A M aA aA= − × + = + −i i j k i j k
Resolve into components.Σ = &G GM H
(a) 2 2 20
1 1: cos sin
2 4M mr α θ θ = +
i
2
2 28 10 1 118 cos 20 sin 20
32.2 12 2 4α = ° + °
221.618 rad/sα =
( )2222 rad/s= iαααα "
(b) 21: 2 sin cos
4zaA mr α θ θ=j
( )
( )
2
28 10
221.618 sin 20 cos20sin cos 32.2 12
0.92167 lb208 812
zmr
Aa
α θ θ ° ° = = =
: 2 0 0y yaA A− = =k ( )0.922 lb=A k"
( )0.922 lb= −B k "
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 72.
Length of rod: 8 8
2.76106 ft12 12
L π= + =
Angular velocity: 0ω= =iωωωω
Angular acceleration: α= iαααα
Angular momentum: ω ω= −G x xzI IH i k
Let the reference frame Gxyz be rotating with angular velocity
ω= = iΩ ωΩ ωΩ ωΩ ω
Rate of change of angular momentum: ( )= + ×& &G G GGxyz
H H HΩΩΩΩ
( )G x x xz x x xzI I I Iα α ω ω ω= − + × −H i k i i k&
2x xz xzI I Iα ω α= + −i j k
Since the mass center G lies on the rotation axis, 0, 0 8 in. 4 in. 1 ftb= = = + =v a
Σ = + = = −m mF a A B a B A
( ) ( )0 0 2Σ = + − × + × = − ×G M b b M bM i i A i B i i A
( ) ( )0 02 2 2= − × + = + −y z z yM b A A M bA bAi i j k i j
Set Σ = &G GM H and resolve into components.
0: α= xM Ii 2
2: 2 2
ωω= = = −xzz xz z z
IbA I A B
bj
: 2 2
αα− = − = = −xzy xz y y
IbA I A B
bk
Calculation of xI and :xzI
Let mass per unit lengthρ = = m
L
For portions AC and DB,
0, 0= =x xzI I
For portion CG use polar coordinate .θ
continued
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( )1 cos , sin θ θ ρ θ= − − = − =x r z r dm rd
2 2 2 30
sin2xI z dm r rd r
π πθρ θ ρ= = =∫ ∫
( )2 30
1 cos sin 2xzI xzdm r rd rπ θ θρ θ ρ= = − =∫ ∫
Likewise, for portion GD 3 3, 22
π ρ ρ= =x xzI r I r
Total: 3 3
3 4,
ππρ= = =x xzmr mr
I r IL L
Data: 21.6 40.049689 lb s /ft, 4 in. ft
32.2 12
Wm r =
g= = = ⋅ =
( )
3
2
40.049689
12 0.0020940 lb s ft2.76106xI
π = = ⋅ ⋅
( ) ( )
3
2
44 0.049689
120.0026661 lb s ft
2.76106xzI
= = ⋅ ⋅
(a) ( )( )0 0.0020940 150xM I α= = 0 0.314 lb ftM = ⋅ "
(b)2
02xz
z zI
A Bb
ω= = = −
( ) ( )
( ) ( )0.0026661 150
0.2002 1y yA B= = = −
( )0.200 lb=A j"
( )0.200 lb= −B j"
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 73.
Fixed axis rotation with constant angular acceleration. , α α ω ω= =i i
2 20 0
1 12 2
t t tθ θ ω α α= + + = ( ) 22 2
2 22 3.1416 rad/s2t
πθα = = =
0ω =
Use centroidal axes x, y, z with origin at C. C x xy xzI I Iω ω ω= − −H i j k
Let the reference frame Cxyz rotate with angular velocity ω= = iΩ ω
( ) 2 2C C C x xy xz xz xyCxyz
I I I I Iα α α ω ω= + × = − − + −H H Ω H i j k j k! !
Required moments and products of inertia. Let mass per unit areamA
ρ = =
mass area 200mm 0.2mI I rρ= = =
Part A xI xyI xzI
21
2rπ 41
8rπ 42
3r− 0
21
2rπ 41
8rπ 0 42
3r−
21
2rπ 41
8rπ 0 42
3r−
21
2rπ 41
8rπ 42
3r− 0
Σ 22 rπ 412
rπ 443
r− 443
r−
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( )2
2 26 23.873 kg/m
2 2 0.2mr
ρπ π
= = =
( ) ( )4 2123.873 0.2 0.06 kg m2xI π = = ⋅
( ) ( )4 2423.873 0.2 0.05093 kg m3xyI = − = − ⋅
( ) ( )4 2423.873 0.2 0.05093 kg m3xzI = − = − ⋅
Since the mass center lies on the rotation axis, 0=a
eff 0mΣ = + = Σ = =F A B F a = −A B
( ) ( )0 0 2C y zM b b M b B BΣ = + − × + × = + × +M i i A i B i i j k
0 2 2z yM bB bB= − +i j k where 2 1.0 mb =
C CMΣ = H! Resolve into components.
( )( )0: 0.06 3.1416xM I α= =i (a) ( )0 0.1885 N m= ⋅M i!
2: 2 z xy xzb B I Iα ω− = − +j
( )( )0.05093 3.1416 00.1600 N
1.0zB− − +
= − = − 0.1600 NzA =
2: 2 y xz xybB I Iα ω= − −k
( )( )0.05093 3.1416 00.1600 N
1.0yB− +
= − = 0.1600 NyA = −
(b) ( ) ( )0.1600 N 0.1600 N= − +A j k !
( ) ( )0.1600 N 0.1600 N= −B j k!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 74.
Fixed axis rotation with constant angular acceleration. , α α ω ω= =i i
2 20 0
1 1
2 2θ θ ω α α= + + =t t t
( ) 22 2
2 223.1416 rad/s
2t
πθα = = =
( )( )0 3.1416 2 6.2832 rad/st tω ω α α= + = = =
Use centroidal axes x, y, z with origin at C. C x xy xzI I Iω ω ω= − −H i j k
Let the reference frame Cxyz rotate with angular velocity ω= = iΩ ωΩ ωΩ ωΩ ω
( ) 2 2C C C x xy xz xz xyCxyz
I I I I Iα α α ω ω= + × = − − + −H H H i j k j k& & ΩΩΩΩ
Required moments and products of inertia. Let mass per unit aream
Aρ = =
mass area 200 mm 0.2 mI I rρ= = =
Part A xI xyI xzI
21
2rπ 41
8rπ 42
3r− 0
21
2rπ 41
8rπ 0 42
3r−
21
2rπ 41
8rπ 0 42
3r−
21
2rπ 41
8rπ 42
3r− 0
∑ 22 rπ 41
2rπ 44
3r− 44
3r−
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( )2
2 2
623.873 kg/m
2 2 0.2
m
rρ
π π= = =
( ) ( )4 2123.873 0.2 0.06kg m
2xI π = = ⋅
( ) ( )4 2423.873 0.2 0.05093kg m
3xyI = − = − ⋅
( ) ( )4 2423.873 0.2 0.05093 kg m
3xzI = − = − ⋅
Since the mass center lies on the rotation axis, 0=a
eff 0mΣ = + = Σ = =F A B F a = −A B
( ) ( )0 0 2C y zM b b M b B BΣ = + − × + × = + × +M i i A i B i i j k
0 2 2z yM bB bB= − +i j k where 2 1.0 mb =
C CMΣ = H& Resolve into components.
( )( )0: 0.06 3.1416xM I α= =i 0 0.1885 N mM = ⋅
2: 2 z xy xzb B I Iα ω− = − +j
( )( ) ( )( )20.05093 3.1416 0.05093 6.2832
1.851 N,1.0zB
− − + −= − = 1.851 NzA = −
2: 2 y xz xybB I Iα ω= − −k
( )( ) ( )( )20.05093 3.1416 0.05093 6.2832
2.17 N,1.0yB
− + −= − = 2.17 NyA = −
( ) ( )2.17 N 1.851 N= − −A j k"
( ) ( )2.17 N 1.851 N= +B j k"
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 75.
Mass of sheet metal: 1.5kg.m =
Sheet metal dimension: 0.120 mb =
Area of sheet metal: 2 2 2 2 2 21 13 0.432m
2 2A b b b b b= + + + = =
Let
21.534.722 kg/m mass per unit area
0.0432
m
Aρ = = = =
Moments and products of inertia: ( ) ( )areamassI Iρ=
xy plane (rectangles)
4 4 41 1 2
3 3 3xI b b b= + =
( )( )442 234.722 0.120
3 3xI bρ= =
3 24.8 10 kg m−= × ⋅
( ) ( )2 2 43 1 5 1 1
2 2 2 2 2xyI b b b b b b b = + − = −
( )( )441 134.722 0.120
2 2xyI bρ= − = −
3 23.6 10 kg m−= − × ⋅
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xz plane (triangles)
4 4 41 1 1
12 12 6xI b b b= + =
( )( )441 134.722 0.120
6 6xI bρ= =
3 21.2 10 kg m−= × ⋅
For calculation of ,xzI use pairs of elements 1dA and 2:dA 2 1dA dA=
( ) ( ) ( ) 21 2 1 0
4 2 22 2
bxz
z zI x dA b x dA b x zdA b x z dx
= ∫ + ∫ − − = − ∫ − = − −
∫
But .z x=
Hence, ( )2 3 4 4 40
2 1 52
3 4 12a
xzI bx x dx b b b = − − = − − = −
∫
( )( )44 3 25 534.722 0.120 3.0 10 kg m
12 12xzI bρ −= − = − = − × ⋅
Total for xI 3 3 3 24.8 10 1.2 10 6.0 10 kg mxI − − −= × + × = × ⋅
The mass center lies on the rotation axis, therefore, 0=a
0F mΣ = + = =A B a = −A B
A x xy xzI I Iω ω ω= − −H i j k ,ω α= =i α iωωωω
Let the frame of reference Axyz be rotating with angular velocity .ω= = iΩ ωΩ ωΩ ωΩ ω
( )A A A AAxyzΣ = = + ×M H H H& & ΩΩΩΩ
( ) ( )0 4 y z x xy xz x xy xzM b B B I I I I I Iα α α ω ω ω ω+ × + = − − + × − −i i j k i j k i i j k
( ) ( )2 20 4 4z y x xy xz xz xyM bB bB I I I I Iα α ω α ω− + = − − − +i j k i j k
Resolve into components and solve for and .y zB B
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0: xM I α=i
( )2
: 4
xy xzz
I IB
b
α ω−=j
( )2
: 4
xz xyy
I IB
b
α ω+= −k
Data: 2150 rad/s , 0, 0.120 mbα ω= = =
(a) ( )( )30 6.0 10 150 0.9 N mM −= × = ⋅ ( )0 0.900 N m= ⋅M i"
(b) ( )( )
( )( )
33.6 10 150 01.125 N
4 0.120zB−− × −
= = −
( )( )( )( )
33.0 10 150 00.9375 N
4 0.120yB−− × +
= − =
0.9375 Ny yA B= − = −
1.125 Nz zA B= − =
( ) ( )0.938 N 1.125 N= − +A j k "
( ) ( )0.938 N 1.125 N= −B j k"
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 76.
The sheet metal component rotates about the fixed z axis with angular acceleration ( )212 rad/s .kα =
(a) Angular velocity at t = 0.6 s.
( )( )0 0 12 0.6 7.2 rad/stω ω α= + = + =
( )7.20 rad/s kω = !
(b) Dynamic reactions. Equations (18.29) of the textbook apply. These are relisted below as equations (1), (2), and (3).
2x xz yzM I Iα ωΣ = − + (1)
2y yz xzM I Iα ωΣ = − − (2)
z zM I αΣ = (3)
Calculation of the required moment and products of inertia. Total mass: 600g 0.6kgm = =
Total area: ( ) ( )( ) ( )2 2 3 21 10.075 0.150 0.075 0.075 16.875 10 m2 2
A −= + + = ×
Let ρ be the mass per unit area. 235.556 kg/mmA
ρ = =
The component is comprised of 3 parts: triangle 1, triangle 2, and rectangle 3 as shown. Let the lengths of 75 mm be labeled b. Triangle 1. The equation of the upper edge is
2by z= −
Use elements of width dz and height y
dm y dzρ= ( ) 2el
112zdI y dm=
( )el0xzdI = ( )el
0yzdI =
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Coordinates of the element mass center:
el ,x b= − el1 ,2
y y= elz z=
( ) el elelxz xzdI dI x z dm= +
( ) ( )02bb z ydz b z z dzρ ρ = + − = − −
42
2
12 12
b
xz bbI b z z dz bρ ρ
−
= − − =
∫
( ) el elelyz yzdI dI y z dm= +
( )21 10
2 2 2by z ydz z z dzρ ρ = + = −
2
42
2
1 12 2 24
b
yz bbI z zdz bρ ρ
−
= − = −
∫
( ) ( )2 2el elelz zdI dI x y dm= + +
2 2 2 2 31 1 112 4 3iy b y y dz b y y dzρ ρ = + + = +
3 2 2 313 5 1 124 4 2 3
b b z bz z dzρ = − + −
3 2 2 3 42
2
13 3 1 1 724 4 2 3 12
b
z bI b b z bz z dz bρ ρ−
= − + − =
∫
Applying the data,
( )( )4 6 21 35.556 0.075 93.75 10 kg m12xzI −= = × ⋅
( )( )4 6 21 35.556 0.075 46.875 10 kg m24yzI −= − = − × ⋅
( )( )4 6 27 35.556 0.075 656.25 10 kg m12zI −= = × ⋅
Triangle 2. The equation of the lower edge is .2by z = − −
Use elements of width dz and height y.
( ) ( ) ( )2el el el
1, , 0, 012z zx yzdm ydz dI y dm dI dIρ= − = = =
continued
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Coordinates of the element mass center:
el ,x b= el1 ,2
y y= elz z=
The integrals for Ixz, Iyz, and Iz turn out to be the same as those of triangle 1.
6 2 6 2 6 293.75 10 kg m , 46.875 10 kg , 656.25 10 kg mmxz yz zI I I− − −= × ⋅ = − × = × ⋅⋅
Rectangle 3. Area: ( )( ) 3 20.150 0.075 11.25 10 mA −= = ×
Mass: 3400 10 kgm Aρ −= = ×
0,xzI = 0yzI =
( ) ( )( )2 23 6 21 12 400 10 0.150 750 10 kg m12 12zI m b − −= = × = × ⋅
Totals. 6 2187.5 10 kg mxz xzI I −= Σ = × ⋅
6 293.75 10 kg myz yzI I −= Σ = − × ⋅
6 22062.5 10 kg mz zI I −= Σ = × ⋅
Since the mass center lies on the fixed axis, the acceleration a of the mass center is zero. 0mΣ = =F a
The reactions at A and B form a couple. = −B A
Let x yA A= +A i j
Resultant couple acting on the body:
( ) 0+x yc A A M= × +M k i j k
0+ +y xcA cA M= − i j k
From (1), 2
y xz yzcA I Iα ω− = − +
( )( ) ( )( )26 623
187.5 10 12 93.75 10 7.247.4 10 N
0.150 0.150yzxz
yIIA
c cωα
− −−
× − ×= − = − = ×
From (2), 2x yz xzcA I Iα ω= − −
( )( ) ( )( )26 623
93.75 10 12 187.5 10 7.257.3 10 N
0.150 0.150yz xz
xI IA
c cα ω
− −−
− × ×= − − = − − = − ×
( ) ( )3 357.3 10 N + 47.3 10 N− −= − × ×A i j !
( ) ( )3 357.3 10 N 47.3 10 N− −= × − ×B i j !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 77.
For each wheel,
65 mph 95.333 ft/s, 0xv ω= = =
95.333
0.21185 rad/s450y
vωρ
= = =
23 23
in. 0.95833 ft2 2 24
dr = = = =
( )( )2
2 2 248 0.750.83851 lb s ft
32.2= = = = ⋅ ⋅z
WI mk k
g
95.333
99.478 rad/s0.95833
= − = − = −zv
rω
G x x y y z z y y z zI I I I Iω ω ω ω ω= + + = +H i j k j k
Let reference frame Gxyz be rotating with angular velocity .yω= jΩΩΩΩ
( ) ( )0G G G y y y z z z z yGxyzI I Iω ω ω ω ω= + × = + × + =H H H j j k i& & ΩΩΩΩ
( )( )( ) ( )0.83851 99.478 0.21185 17.671 lb ft= − = − ⋅&GH i i
Let O be the point at the center of the axle. For the two wheels plus the axle,
( )35.342 lb ftO G G= + = − ⋅H H H i& & &
The distance between the wheels is 4.5 ft.
4.5 4.5O y yF F= × = −M k j i
Set O O=M H& and solve for .yF
35.342
7.85 lb4.5yF
−= =−
7.85 lbyF = !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 78.
Let the x axis lie along the axle AB and the y axis be vertical.
( )2 100001047.2 rad/s, 500 mph 733.33 ft/s
60= = = =x v
πω
733.332250 ft, 0.32593 rad/s 02250
= = − = − = − =y zvρ ω ωρ
Angular momentum: G x x y y z z x x y yI I I I Iω ω ω ω ω= + + = +H i j k i j
Let the reference frame Gxyz be turning about the y axis with angular velocity .yω= jΩ
( ) ( )G G G y x x y yGxyzH I Iω ω ω= + × = × +H j i j! ! Ω Η
x x yI ω ω= − k
Data for the disk: 7
3 216 13.587 10 lb s /ft32.2
m −= = × ⋅
( )2
2 3 6 21 1 213.587 10 188.708 10 lb s ft2 2 12xI mr − − = = × = × ⋅ ⋅
( )( )( ) ( )6188.708 10 1047.2 0.32593 0.06441 lb ftG G−= = − × − = ⋅M H k k!
The spring forces AF and BF exerted on the yoke provide the couple .GM The force exerted by spring B is upward.
Let . Then .B AF F= = −F j F j
/5 0.41667
12G B A F F F= × = × =M r i j i j k
From , 0.41667 0.06441 0.15458 lb.G G F F= = =M H!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Compression of spring B:
0.15458 0.0038645 ft 0.04637 in.40B
Fk
δ = = = =
Point B moves 0.0464 in. down. Point A moves 0.0464 in. up
Turning angle for yoke:
0.4637 0.4637 0.01855 rad5
θ += =
1.063θ = ° !
Point moves .A up !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 79.
1 1ω= iωωωω ( )
12 1800
188.5 rad/s60
π= =ωωωω
Angular velocity: 1 2ω ω= +i jωωωω
Angular momentum: 1 2G x yI Iω ω= +H i j
Let the reference frame be rotating with angular velocity 2 .ω= jΩΩΩΩ
( ) ( )2 1 2 1 20G G G x y xGxyzI I Iω ω ω ω ω= + × = + × + = −H H H j i j k& & ΩΩΩΩ
Assume that the acceleration of the mass center is negligible. Then the dynamic reactions at A and B reduce to a couple.
= −A B
( )y z z yb b B B b B b B= × = × + = − +M i B i j k j k
G=M H& Resolve into components.
: 0zb B− =j 0,zB = 0zA =
1 2: y xb B I ω ω= −k 2
1 2 1 2x xy
I mkB
b b
ω ω ω ω= − = −
( )( ) ( )( )230.300 75 10 188.5 0.61.527 N,
0.125yB−×
= − = − 1.527 NyA =
( )1.527 N=A j!
( )1.527 N= −B j!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 80.
Choose axes x, y, z as shown.
Angular velocity of airplane: 2vω ρ=
where 540 km/h 150 m/s, 600 mv ρ= = =
2 2 2150
0.25 rad/s, 600
ω ω= = = kωωωω
Angular velocity of propeller relative to the airplane: 1 1ω= iωωωω
( )( )1
2 1600167.552 rad/s
60
πω = =
Angular momentum of propeller: 1 2G x zI Iω ω= +H i k
Let the reference frame Gxyz be rotating with angular velocity 2 .ω= kΩΩΩΩ
( ) ( )2 1 2 1 20G G G x z xGxyzI I Iω ω ω ω ω= + × = + × + = −H H H k i k j& & ΩΩΩΩ
Couple exerted on the propeller: 1 2G xI ω ω= = −M H j&
Couple exerted by the propeller: 1 2xI ω ω′ = − =M M j (1)
Data for the propeller: 160 kgm =
( ) ( )22 2160 0.8 102.4 kg mx xI mk= = = ⋅
Using Equation (1), ( ) ( ) ( ) ( )102.4 167.552 0.25 4289 N m= = ⋅′M k k
Magnitude of couple: 4290 N mM = ⋅ !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 81.
Let the x axis be a horizontal axis directed along the engine mounting, i.e., longitudinally for rear-wheel drive and transversely for front-wheel drive.
Let the y axis be vertical.
The angular velocity of the automobile, 2,ωωωω is equal to ( )/ ,v ρ j where 60 mph 88 ft/s and 600 ft.v ρ= = =
( )288
0.146667 rad/s600
= =j jωωωω
Angular velocity of the fly wheel relative to the automobile: 1 1ω= iωωωω
where ( )
12 2700
282.74 rad/s60
πω = =
Angular momentum of fly wheel: 1G x y yI Iω ω= +H i j
Let the reference frame Gxyz be rotating with angular velocity 2ω= jΩΩΩΩ
( ) ( )2 1 2 1 20G G G x y xGxyzI I Iω ω ω ω ω= + × = + × + = −H H H j i j k& & ΩΩΩΩ
Couple exerted by the shaft on the fly wheel: 1 2xI ω ω= −M k
Couple exerted by the fly wheel on the shaft: 1 2xI ω ω′ = − =M M k (1)
Data for fly wheel: ( ) ( ) ( )22 30.284 lb/in 20 in. 0.75 in. 66.916 lb4 4
W d tπ πγ = = =
266.9162.0781 lb s /ft
32.2
Wm
g= = = ⋅
For a circular plate, ( )2
2 21 1 102.0781 0.72157 lb s ft
2 2 12xI mr = = = ⋅ ⋅
Using Equation (1), ( )( )( ) ( )0.72157 282.74 0.146667 29.9 lb ft′ = = ⋅M k k
(a) Magnitude of couple for rear-wheel drive: 29.9 lb ftM ′ = ⋅ !
(b) For front-wheel drive: 29.9 lb ftM ′ = ⋅ !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 82.
Angular velocity: 1,xω ω= 0,yω = 2.zω ω=
2+ω ω1i kω =ω =ω =ω =
Angular momentum: + +O x x y y z zI I Iω ω ω=H i j k
1 2+x zI Iω ω= i k
Let frame Oxyz be rotating with angular velocity 1 .ω= iΩΩΩΩ
Rate of change of angular momentum.
( )O O OOxyz= + ×H H& & Ω ΗΩ ΗΩ ΗΩ Η
( )1 2 1 1 2
21 2 1 2
+ + +
10 0 0 =
2
x z x z
z
I I I I
I mr
ω ω ω ω ω
ω ω ω ω
= ×
= + + − −
i k i i k
j j
& &
Dynamic reaction couple: = OM H&
( )( )2
21 2
1 1 5 43 6
2 2 32.2 12 = −
mr =ω ω −M j j
( )= 0.1553 lb ft− ⋅M j!
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 83.
Let point O be the midpoint of axle AB. Choose principal axes , ,x y z′ ′ ′ with origin at point O.
2 21 1, ,
12 3x zI ma I ma′ ′= =
25
12y x zI I I ma′ ′ ′= + =
sin cosω β ω β′ ′= − +i jωωωω
O x x y y z zI I Iω ω ω′ ′ ′ ′ ′′ ′= + +H i j k
sinxI ω β= − i
Let the reference frame Ox y z′ ′ ′ be rotating about the fixed point O with
angular velocity .Ω = ωΩ = ωΩ = ωΩ = ω
( ) 0O O O OOx y z′ ′ ′= + × = + ×H H Η H& & Ω ωΩ ωΩ ωΩ ω
( ) ( )sin cos sin cosx yI Iω β ω β ω β ω β′ ′′ ′ ′ ′= − + × − +i j i j
( ) 2 sin cosy xI I ω β β′ ′= − − k
21sin cos
3ma β β= − k
cos2O Oa
W β= − =M k H&
22sin
3W ma mgω β= =
22sin
3g aω β=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
(a) ( )( )
( )( )( )2 2
3 9.813sin 0.45417
2 2 0.225 12
g
aβ
ω= = = 27.0β = °!
(b) Set 90 , sin 1β β= ° =
( )( )
( )( )2 3 9.813
65.42 2 0.225
g
aω = = = 8.09 rad/sω = !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 84.
Let point O be the midpoint of axle AB. Choose principal axes
, ,x y z′ ′ ′ with origin at point O.
2 21 1, ,12 3x zI ma I ma′ ′= =
2512y x zI I I ma′ ′ ′= + =
sin cosω β ω β′ ′= − +i jω
O x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′= + +H i j k
sinxI ω β= − i
Let the reference frame Ox y z′ ′ ′ be rotating about the fixed point O with angular velocity .Ω = ω
( ) 0O O O OOx y z′ ′ ′= + × = + ×H H Η H! ! Ω ω
( ) ( )sin cos sin cosx yI Iω β ω β ω β ω β′ ′′ ′ ′ ′= − + × − +i j i j
( ) 2 sin cosy xI I ω β β′ ′= − − k
21 sin cos3
ma β β= − k
cos2O OaW β= − =M k H!
22 sin3
W ma mgω β= =
22 sin3
g aω β=
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
(a) ( )( )( )( ) ( )22 3 9.813 56.638 rad/s
2 sin 2 0.3 sin 60g
aω
β= = =
°
7.53 rad/sω = !
(b) Set 90 , sin 1β β= ° =
( )( )( )( ) ( )22 3 9.813 49.05 rad/s
2 2 0.3ga
ω = = = 7.00 rad/sω = !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 85.
Choose principal axes x, y, z with origin at the fixed point A.
2 2 2 2 21 32 , ,
2 2x y zI mr mr mr I mr I mr= + = = =
sin cosω β ω β= +i jωωωω
A x x y y z zI I Iω ω ω= + +H i j k
sin cosx yI Iω β ω β= +i j
Let the reference frame Axyz be rotating with angular velocity .Ω = ωΩ = ωΩ = ωΩ = ω
( ) 0A A A AAxyz= + × = + ×H H Η H& & Ω ωΩ ωΩ ωΩ ω
( ) ( )sin cos sin sinx yI Iω β ω β ω β ω β= + × +i j i j
( ) 2 2 23sin cos sin cos
2y xI I mrω β β ω β β= − = −k k
( )sinA Amgr βΣ = − =M k H&
23cos
2g rω β=
(a) ( )
( ) ( )2 2
2 32.22cos 0.322
83 3 1012
g
rβ
ω= = =
71.2β = °!
(b) Set 0 , cos 1β β= ° =
( )( )( )
2 2 32.2232.2
83 312
g
rω = = =
5.67 rad/sω = !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 86.
Choose principal axes x, y, z with origin at the fixed point A.
2 2 2 2 21 32 , ,
2 2x y zI mr mr mr I mr I mr= + = = =
sin cosω β ω β= +i jωωωω
A x x y y z zI I Iω ω ω= + +H i j k
sin cosx yI Iω β ω β= +i j
Let the reference frame Axyz be rotating with angular velocity .Ω = ωΩ = ωΩ = ωΩ = ω
( ) 0A A A AAxyz= + × = + ×H H Η H& & Ω ωΩ ωΩ ωΩ ω
( ) ( )sin cos sin sinx yI Iω β ω β ω β ω β= + × +i j i j
( ) 2 2 23sin cos sin cos
2y xI I mrω β β ω β β= − = −k k
( )sinA Amgr βΣ = − =M k H&
23cos
2g rω β=
(a) ( )( )
( )( )22 2 32.22
30.358 rad/s123 cos 3 cos 4512
g
rω
β= = =
°
5.51 rad/sω = !
(b) Set 0, cos 1β β= =
( )( )( )
( )22 2 32.2221.467 rad/s
123 312
g
rω = = =
4.63 rad/sω = !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 87.
20 430 , 20 in. ft, 4 in. ft
12 12L rβ = ° = = = =
Choose principal axes x, y, z as shown.
Kinematics: 1 1 1 2 2sin cosω β ω β ω= + =i j jω ωω ωω ωω ω
( )1 2 1 1 2sin cosω β ω β ω= + = + +i jω ω ωω ω ωω ω ωω ω ω
1 1 2sin cosx yω ω β ω ω β ω= = +
1 / 1 / 1 sinG G D G D Lω β= × = × = −v r j r kω ωω ωω ωω ω
21 1 sinG G Lω β= × =a vωωωω
/C G C G= + ×v v rωωωω
( ) ( )10 sin x yL rω β ω ω= − + + × −k i j i
1 sin yL rω β ω= − +k k
1 sinyL
rω ω β=
Angular momentum: G x x y yI Iω ω= +H i j
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Let the reference frame Dxyz be rotating with angular velocity 1.=Ω ωΩ ωΩ ωΩ ω
( ) ( ) ( )
( )1 1
2 21 1 1
0 sin cos
1 1sin cos sin cos
2 4
G G G x x y yGxyz
y y x x y x
I I
I I mr mr
ω β ω β ω ω
ω ω β ω ω β ω β ω β ω
= + × = + + × +
= − = −
H H Η i j i j
k k
& & ΩΩΩΩ
Moments about D:
sin ,D Fd mgL β= −M k k
where 2 2d L r= +
( ) /effD G G D Gm= + ×M H r a&
2 21 sin cosG m Lω β β= +H k&
Equating ( )effD D=M M and taking the z component,
2 2 2 2 2 21 1
1 1sin sin sin cos sin cos
2 4CLF d mgL mr mr m Lr
β β β β ω ω β β − = − +
2 2 21
1 1sin sin cos cos
2 4m rL r Lω β β β β = − −
Set 210 and solve for :F ω=
( )21 2 2
2 2
2032.2
121 1 20 1 4 1 4 20cos cos sin cos30 cos30 sin 304 2 12 4 12 2 12 12
gL
L r rLω
β β β
= =
+ − ° + ° − °
23.427= 1 4.84 rad/sω = !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 88.
20 430 , 20 in. ft, 4 in. ft
12 12L rβ = ° = = = =
Choose principal axes x, y, z as shown.
Kinematics: 1 1 1 2 2sin cosω β ω β ω= + =i j jω ωω ωω ωω ω
( )1 2 1 1 2sin cosω β ω β ω= + = + +i jω ω ωω ω ωω ω ωω ω ω
1 1 2sin cosx yω ω β ω ω β ω= = +
1 / 1 / 1 sinG G D G D Lω β= × = × = −v r j r kω ωω ωω ωω ω
21 1 sinG G Lω β= × =a vωωωω
/C G C G= + ×v v rωωωω
( ) ( )10 sin x yL rω β ω ω= − + + × −k i j i
1 sin yL rω β ω= − +k k
1 sinyL
rω ω β=
Angular momentum: G x x y yI Iω ω= +H i j
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Let the reference frame Dxyz be rotating with angular velocity 1.=Ω ωΩ ωΩ ωΩ ω
( ) ( ) ( )1 10 sin cosG G G x x y yGxyzI Iω β ω β ω ω= + × = + + × +H H Η i j i j& & ΩΩΩΩ
( ) 2 21 1 1
1 1sin cos sin cos
2 4y y x x y xI I mr mrω ω β ω ω β ω β ω β ω = − = −
k k
Moments about D:
sin ,D Fd mgL β= −M k k
where 2 2d L r= +
( ) /effD G G D Gm= + ×M H r a&
2 21 sin cosG m Lω β β= +H k&
Equating ( )effD D=M M and taking the z component,
2 2 2 2 2 21 1
1 1sin sin sin cos sin cos
2 4CLF d mgL mr mr m Lr
β β β β ω ω β β − = − +
2 2 21
1 1sin sin cos cos
2 4m rL r Lω β β β β = − −
Solving for ,CF
2 2 21
sin 1 1cos cos sin
4 2Cm
F gL L r rLd
β ω β β β = − + −
Additional data: 21
20.062112 lb s /ft, 4 rad/s
32.2m ω= = ⋅ =
2 220 4
1.69967 ft12 12
d = + =
continued
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( ) ( ) ( )2 2
20.061112 sin 30 20 20 1 4 1 20 432.2 4 cos30 cos30 sin 30
1.69967 12 12 4 20 2 12 12CF ° = − ° + ° − °
0.311 lb=
1 1 4tan 30 tan 18.7
20
r
Lα β α− − = − = ° − = °
0.311 lb 18.7°!
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Chapter 18, Solution 89.
Let 0.3 m, and 0.1 m.AB L BC b= = = =
Choose , ,x y z axes as shown. 210,12x y zI I I mL≈ = =
Angular velocity: sin 30 cos30ω ω= ° + °i jω
Angular momentum of rod AB about its mass center G:
cos30G x x y y z z yI I I Iω ω ω ω= + + = °H i j k j
Let the reference frame Gxyz be rotating with angular velocity .=Ω ω
( )G G GGxyz= + ×H H Η! ! Ω
( )0 sin 30 cos30 cos30yIω ω ω= + ° + ° × °i j j
2 2 23sin 30 cos3048yI mLω ω= ° ° =k k
Radius of circular path of point G: cos30 0.22990 m2Lr b= ° + =
Acceleration of the mass center: 2rω=a Equations of motion:
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2cos30 sin 30
2 2B GL Lmg mrω Σ = ° = ° +
M k k H!
2 23 1 34 4 48
mgL mLr mL ω
= +
k k
23 1 34 4 48
g r L ω
= +
( ) ( ) ( ) 23 1 39.81 0.22990 0.34 4 48
ω
= +
2 62.194ω = 7.89 rad/sω = !
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Chapter 18, Solution 90.
Let 0.3 m, and 0.1 m.AB L BC b= = = =
Choose , ,x y z axes as shown. 210,
12x y zI I I mL≈ = =
Angular velocity: sin 30 cos30ω ω= − ° + °i jωωωω
Angular momentum of rod AB about its mass center G:
cos30G x x y y z z yI I I Iω ω ω ω= + + = °H i j k j
Let the reference frame Gxyz be rotating with angular velocity .Ω = ωΩ = ωΩ = ωΩ = ω
( )G G GGxyz= + ×H H Η& & ΩΩΩΩ
( )0 sin 30 cos30 cos30yIω ω ω= + − ° + ° × °i j j
2 2 23sin 30 cos30
48yI mLω ω= − ° ° = −k k
Radius of circular path of point G: cos30 0.029904 m2
Lr b= ° − =
Acceleration of the mass center: 2rω=a
Equations of motion:
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2cos30 sin 30
2 2B GL L
mg mrω Σ = − ° = − ° +
M k k H&
2 23 1 3
4 4 48mgL mLr mL ω
− = − +
k k
23 1 3
4 4 48g r L ω
= +
( ) ( ) ( ) 23 1 39.81 0.029904 0.3
4 4 48ω
= +
2 232.11ω = 15.24 rad/sω = !
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Chapter 18, Solution 91.
Angular velocity: 1 2ω ω= +ω i k
Angular momentum: 1 2C x x y y z z x zI I I I Iω ω ω ω ω= + + = +H i j k i
Let the reference frame Cxyz be rotating with angular velocity 1ω=Ω i
( ) ( )1 1 2 1 20C C C x z zCxyzI I Iω ω ω ω ω= + × = + × + = −H H Ω H i i k j& &
Acceleration of mass center: 0=a
Equivalence of external and effective forces.
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0mΣ = + = = −F a A B B A
The resultant of A and B is a couple. Its moment is
( ) ( )/ 2 2 2A B y z z ya A A aA aA× = − × + = −r A i j k j k
/A B C× =r A H&
components: 1 21 2: 2
2z
z z zI
aA I Aa
ω ωω ω= − = −j
: 2 0yaA− =k 0yA =
Data : 21 2
1 1
2 4z zI ma A maω ω= = −
1 21
4maω ω= −A k !
1 21
4maω ω=B k !
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Chapter 18, Solution 92.
Angular velocity of the disk. ( ) ( )1 2 5 rad/s 15 rad/sω ω= + = +ω j k j k
Mass of disk. 210 0.31056 lb s /ft32.2
= = = ⋅Wmg
Moments of inertia about principal axes passing through the mass center.
( )2
2 21 1 60.31056 0.019410 lb s ft4 4 12x yI I mr = = = = ⋅ ⋅
( )2
2 21 1 60.31056 0.038820 lb s ft2 2 12zI mr = = = ⋅ ⋅
Angular momentum about mass center C.
( )( ) ( )( )0 0.019410 5 0.038820 15C x x y y z zI I Iω ω ω= + + = + +H i j k j k
( ) ( )0.09705 lb s ft 0.5823 lb s ft= ⋅ ⋅ + ⋅ ⋅j k
Rate of change of HC . Let the frame Axyz be turning with angular velocity 1 .ω=Ω j
( ) 0C C C CAxyz= + × = + ×H H Ω H Ω H! !
( ) ( )5 0.09705 0.5823 2.9115 lb ft= × + = ⋅j j k i
Position vector of point C. ( ) ( )/18 9 1.5 ft 0.75 ft12 12C A = + = +r i j i j
Velocity of point C, the mass center of the disk.
( ) ( )1 / 5 1.5 0.75 7.5 ft/sC C Aω= × = × + = −v j r j i j k
Acceleration of point C.
( ) ( )21 / 1 0 5 7.5 37.5 ft/sC C A Cα ω= × + × = + × − = −a j r j v j k i
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Effective force at C. ( )( ) ( )0.31056 37.5 11.646 lbCm = − = −a i i
Equivalence of external and effective forces.
Linear components: Cm=A a ( )11.65 lb= −A i !
Moments about A. /A C A C Cm= × +M r a H!
( ) ( )1.5 0.75 11.646 2.9115A = + × − +M i j i i
( ) ( )2.91 lb ft 8.73 lb ftA = ⋅ + ⋅M i k !
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Chapter 18, Solution 93.
Angular velocity: 2 1ω ω= −i kωωωω
Angular momentum: 2 1C x x y y z z x zI I I I Iω ω ω ω ω= + + = −H i j k i k
Let the reference frame Cxyz be rotating with angular velocity 2 .ω= iΩΩΩΩ
( ) ( )2 2 1 2 10C C C x z zCxyzI I Iω ω ω ω ω= + × = + × − =H H H i i k j& & ΩΩΩΩ
Acceleration of mass center:
0=a
mΣ =F a
0A B− =k k
A B=
C C=M H&
2 12 1 z
zI
LB I BL
ω ωω ω= =j j
Data: ( )( )22 6 21 10.3 kg, 0.3 0.050 375 10 kg m
2 2zm I mr −= = = = × ⋅
( )1 2
2 75025 rad/s, 6 rad/s, 0.200 m
60L
πω π ω= = = =
( )( )( )6375 10 6 250.88357 N
0.200A B
π−×= = =
( )0.884 N=A k!
( )0.884 N= −B k!
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Chapter 18, Solution 94.
Angular velocity: 2 1ω ω= −i kωωωω
Angular momentum: 2 1C x x y y z z x zI I I I Iω ω ω ω ω= + + = −H i j k i k
Let the reference frame Cxyz be rotating with angular velocity 2 .ω= iΩΩΩΩ
( ) ( )2 2 1 2 10C C C x z zCxyzI I Iω ω ω ω ω= + × = + × − =H H H i i k j& & ΩΩΩΩ
Acceleration of mass center:
0=a
mΣ =F a
0A B− =k k
A B=
C C=M H&
2 12 1 z
zI
LB I BL
ω ωω ω= =j j
Data: ( )( )22 6 21 10.3 kg, 0.3 0.050 375 10 kg m
2 2zm I mr −= = = = × ⋅
( )1
2 75025 rad/s, 0.200 m
60L
πω π= = =
1 NA B= =
( )( )
( )( )2 61
0.200 1.0
375 10 25z
LB
Iω
ω π−= =
× 2 6.79 rad/sω = !
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Chapter 18, Solution 95.
For disk A: 1 2A ω ω= −j kω
1 20A x x y y z z y zI I I I Iω ω ω ω ω= + + = + −H i j k j j
2 21 2
1 12 4
mr mrω ω= −j k
Let the reference frame Oxyz be rotating with angular velocity 2 .ω= − kΩ
( ) ( ) 2 22 1 2
1 102 4A A AOxyz
mr mrω ω ω = + × = + − × −
H H H k j k! ! Ω
22 1
12
mr ω ω= i
Acceleration of its mass center: 22A bω= −a j
For disk B: 22, , , B A B A B A B bω= = = =H H H H a j! !ω ω
Let the system of particles be disks A and B together with axle AB and shaft CD. Neglect the mass of the axle and the shaft.
A Bm mΣ = +F a a 2 22 2C D b bω ω− + = − +j j j j
D C=
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22 2 1
0 2 1 A BmrcC mr C
cω ωω ωΣ = = + = =M i H H i! !
(a) Data: 5 kg, 0.3 m, 0.6 m,m r c= = =
( ) ( )1 2
2 1200 2 6040 rad/s 2 rad/s
60 60π π
ω π ω π= = = =
( )( ) ( )( )25 0.3 40 2592 N
0.6C
π π= = ( )592 N= −C j!
( )592 N=D j!
(b) For disk A: 1 2 1 2, A A y zI Iω ω ω ω= − − = − −j k H j kω
22 1
1 , 02A A Bmr ω ω= − + =H i H H! ! ! 0= =C D !
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Chapter 18, Solution 96.
For disk A: 1 2A ω ω= −j kωωωω
1 20A x x y y z z y zI I I I Iω ω ω ω ω= + + = + −H i j k j j
2 21 2
1 1
2 4mr mrω ω= −j k
Let the reference frame Oxyz be rotating with angular velocity 2 .ω= − kΩΩΩΩ
( ) ( ) 2 22 1 2
1 10
2 4A A AOxyzmr mrω ω ω = + × = + − × −
H H H k j k& & ΩΩΩΩ
22 1
1
2mr ω ω= i
Acceleration of its mass center: 22A bω= −a j
For disk B: 22, , , B A B A B A B bω= = = =H H H H a j& &ω ωω ωω ωω ω
Let the system of particles be disks A and B together with axle AB and shaft CD.
Neglect the mass of the axle and the shaft.
A Bm mΣ = +F a a
2 22 2C D b bω ω− + = − +j j j j
D C=
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22 2 1
0 2 1 A Bmr
cC mr Cc
ω ωω ωΣ = = + = =M i H H i& &
Solving for 2,ω 2 21
cC
mrω
ω=
Data: 5 kg , 0.3 m, 0.6 mm r c= = =
( )1
2 120040 rad/s, 350 N
60C D
πω π= = = =
( )( )
( )( ) ( )2 2
0.6 3503.7136 rad/s
5 0.3 40ω
π= =
2 35.5 rpmω = !
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Chapter 18, Solution 97.
Use principal axes , , x y z′ ′ as shown.
Moments of inertia: ( )2 213xI m a b′ = +
2 21 1, 3 3y zI ma I mb′ ′= =
Kinematics: 1θ ω=!
2 2 1sin , cos , x y zω ω θ ω ω θ ω ω′ ′ ′= = =
1 2 1 2cos , sin , 0x y zω ω ω θ ω ω ω θ ω′ ′ ′= = − =! ! !
Since the acceleration of the mass center is zero, the resultant force acting on the column CD is zero.
0=R !
Eulers equations of motion for the plate:
( ) ( )1 2 1 2cos cosx x x y z y z x y zM I I I I I Iω ω ω ω ω θ ω ω θ′ ′ ′ ′ ′ ′ ′ ′ ′ ′Σ = − − = − −!
( ) 21 2 1 2
2cos cos3x z yI I I mbω ω θ ω ω θ′ ′ ′= + − =
( ) ( )1 2 1 2sin siny y y z x x z y z xM I I I I I Iω ω ω ω ω θ ω ω θ′ ′ ′ ′ ′ ′ ′Σ = − − = − − −!
( ) 1 2 sin 0x y zI I I ω ω θ′ ′ ′= − − =
( ) ( ) 220 sin cosz z z x y x y x yM I I I I Iω ω ω ω θ θ′ ′ ′ ′ ′ ′ ′Σ = − − = − −!
2 22
1 sin cos3
mb ω θ θ= −
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2 2 21 2 2
2 1cos sin cos3 3
mb mbω ω θ ω θ θ′Σ = −M i k
( )2 2 21 2 2
2 1cos cos sin sin cos3 3
mb mbω ω θ θ θ ω θ θ= + −i j k
Resolve into components: 2 21 2
2 cos3xM mb ω ω θΣ =
2 2 21 2 2
2 1sin cos , sin cos3 3y zM mb M mbω ω θ θ ω θ θΣ = Σ = −
Data: 2100 3.1056 lb s /ft, 2.4 ft32.2
m b= = ⋅ =
1 22 21.0472 rad/s, 0.5236 rad/s6 12π πω ω= = = =
( )( ) ( )( )2 2 22 3.1056 2.4 1.0472 0.5236 cos 6.54cos lb ft3xM θ θΣ = = ⋅
( )( ) ( )( )22 3.1056 2.4 1.0472 0.5236 sin cos 6.54sin cos lb ft3yM θ θ θ θΣ = = ⋅
( )( ) ( )2 21 3.1056 2.4 0.5236 sin cos 1.635sin cos lb ft3zM θ θ θ θΣ = − = − ⋅
( ) ( ) ( )26.54 lb ft cos 6.54 lb ft sin cos 1.635 lb ft sin cosD θ θ θ θ θ= ⋅ + ⋅ − ⋅M i j k !
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Chapter 18, Solution 98.
Use principal axes , , x y z′ ′ as shown.
Moments of inertia: ( )2 21
3xI m a b′ = +
2 21 1,
3 3y zI ma I mb′ ′= =
Kinematics: 1θ ω=&
2 2 1sin , cos , x y zω ω θ ω ω θ ω ω′ ′ ′= = =
1 2 1 2cos , sin , 0x y zω ω ω θ ω ω ω θ ω′ ′ ′= = − =& & &
Euler’s equations of motion for the plate:
( ) ( )1 2 1 2cos cosx x x y z y z x y zM I I I I I Iω ω ω ω ω θ ω ω θ′ ′ ′ ′ ′ ′ ′ ′ ′ ′Σ = − − = − −&
( ) 21 2 1 2
2cos cos
3x z yI I I mbω ω θ ω ω θ′ ′ ′= + − =
( ) ( )1 2 1 2sin siny y y z x x z y z xM I I I I I Iω ω ω ω ω θ ω ω θ′ ′ ′ ′ ′ ′ ′Σ = − − = − − −&
( ) 1 2 sin 0x y zI I I ω ω θ′ ′ ′= − − =
( ) ( ) 220 sin cosz z z x y x y x yM I I I I Iω ω ω ω θ θ′ ′ ′ ′ ′ ′ ′Σ = − − = − −&
2 22
1sin cos
3mb ω θ θ= −
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2 2 21 2 2
2 1cos sin cos
3 3mb mbω ω θ ω θ θ′Σ = −M i k
( )2 2 21 2 2
2 1cos cos sin sin cos
3 3mb mbω ω θ θ θ ω θ θ= + −i j k
Resolve into components: 2 21 2
2cos
3xM mb ω ω θΣ =
2 2 21 2 2
2 1sin cos , sin cos
3 3y zM mb M mbω ω θ θ ω θ θΣ = Σ = −
(a) ,D = ΣM M which is independent of the dimension 2a.
(b) 22 1 2
2sin cos
3zM M mb ω ω θ θ= Σ =
2 21 2
1sin cos
3yM M mb ω θ θ= Σ =
ratio 1 2
2 12
M
M
ωω
=
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Chapter 18, Solution 99.
Angular velocity: 1 2ω ω= +ω i k
Angular momentum: 1 2C x x y y z z x zI I I I Iω ω ω ω ω= + + = +H i j k i
Let the reference frame Cxyz be rotating with angular velocity 1ω=Ω i
( ) 1 2 1C C C x z CCxyzI Iω ω ω= + × = + + ×H H Ω H i k i H! ! ! !
( )1 1 1 2 1 1 20x x z x zI I I I Iα ω ω ω α ω ω= + + × + = −i i i k i j
Acceleration of mass center: 0=a
Equivalence of external and effective forces.
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0mΣ = + = = −F a A B B A
The resultant of A and B is a couple. Its moment is
( ) ( )/ 2 2 2A B y z z ya A A aA aA× = − × + = −r A i j k j k
Resultant moment on rod AB and disk.
1 2 2z y CM aA aA= + − =M i j k H!
components: 1 1: xM I α=i
1 21 2: 2
2z
z z zIaA I A
aω ωω ω= − = −j
: 2 0yaA− =k 0yA =
Data : 2 21 14 2x zI ma I ma= =
(a) Moment 1 .M i
21 1
14
M ma α=i i !
(b) Reactions at A and B. 1 214
mω ω= −A k !
1 214
mω ω=B k !
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Chapter 18, Solution 100.
Angular velocity: 2 1ω ω= −i kωωωω
Angular momentum: 2 1C x x y y z z x zI I I I Iω ω ω ω ω= + + = −H i j k i k
Let the reference frame Cxyz be rotating with angular velocity 2 .ω= iΩΩΩΩ
( ) ( )1 2 2 1C C C z x zCxyzI I Iω ω ω ω= + × = − + × −H H H k i i k& & &ΩΩΩΩ
1 1 2z zI Iω ω ω= − +k j&
Acceleration of mass center: 0=a
mΣ =F a 0+ =A B = −A B
Moments about C : C C=M H&
( ) 1 1 2y z z zL B B I Iω ω ω× + = − +i j k k k&
1 1 2y z z zLB LB I Iω ω ω− = − +k j k k&
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Data: ( )( )22 6 21 10.3 kg, 0.3 0.050 375 10 kg m
2 2zm I mr −= = = = × ⋅
21 2 112 rad/s, 6 rad/s, 4 rad/sω ω ω= = = −&
0.200 mL =
( )( ) ( )( )( )6 60.200 0.200 375 10 4 375 10 12 6y zB B − −− = − × − + ×k j k j
( )( )6375 10 4
0.0075 N0.200yB
−− × −= = 0.0075 NyA = −
( )( )( )6375 10 12 6
0.1350 N0.200zB
−×= = 0.1350 NzA =
( ) ( )0.0075 N 0.1350 N= − +A j k !
( ) ( )0.0075 N 0.1350 N= −B j k !
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Chapter 18, Solution 101.
Angular velocity of the shaft and arm ABC: 2ω= jΩΩΩΩ
Angular velocity of disk C: 2 1 1, 0ω ω ω= + =j k &ωωωω
Its angular momentum about C: 2 1C x x y y z z y zI I I I Iω ω ω ω ω= + + = +H i j k j k
Let the reference frame Axyz be turning with angular velocity .ΩΩΩΩ
( ) ( )2 2 2 1C C C y y zAxyzI I Iω ω ω ω= + × = + × +H H H j j j k& & &ΩΩΩΩ
2 22 1 2 2 1 2
1 1
2 4z yI I mr mrω ω ω ω ω ω= + = +i j i j& &
Velocity and acceleration of the mass center C of the disk:
( )/ 2 2 2C C A b c c bω ω ω= × = × + = −v r j i k i kΩΩΩΩ
( ) ( )2 22 / 2 2 2 2 2C C A C c b b cω ω ω ω ω ω= × + × = − + +a j r j v i k& & &
eff : Resolve into components.x z CA A mΣ = Σ + =F F i k a
( ) ( )2 22 2 2 2 x zA m c b A m b cω ω ω ω= − = − +& &
( )/A A C C A C C Cm b c mΣ = = + × = + + ×M H H r a H i k a& & &
2 2 2 22 1 2
1 1 Resolve into components.
2 4mr m r b cω ω ω = + + +
i j&
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( ) ( )2 2 2 22 1 0 2
1 1
2 4A Ax yM mr M M m r b cω ω ω = = = + +
&
Solving for 2 :ω& 02 2 2 2
2 2 2
1.51 80 1 10 16 124 32.2 4 12 12 12
M
m r b cω = =
+ + + +
&
20.204565 rad/s=
At 5 s,t = ( )( )2 2 0.204565 5 1.022824 rad/stω ω= = =&
After 5 s, let 2 0ω =& so that 2ω is constant.
( )222
80 161.022824 3.4656 lb
32.2 12xA mbω = − = − = −
( )222
80 121.022824 2.5992 lb
32.2 12zA mcω = − = − = −
( ) ( )3.47 lb 2.60 lb= − −R i k !
( ) 0A yM =
( ) ( )( )2
22 1
1 1 80 101.022824 80 70.588 lb ft
2 2 32.2 12A xM mr ω ω = = = ⋅
( )70.6 lb ftA = ⋅M i!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 102.
Angular velocity of the shaft and arm ABC: 2ω= jΩ
Angular velocity of disk C: 2 1 1, 0ω ω ω= + =j k !ω
Its angular momentum about C: 2 1C x x y y z z y zI I I I Iω ω ω ω ω= + + = +H i j k j k
Let the reference frame Axyz be turning with angular velocity .Ω
( ) ( )2 2 2 1C C C y y zAxyzI I Iω ω ω ω= + × = + × +H H H j j j k! ! !Ω
2 22 1 2 2 1 2
1 12 4z yI I mr mrω ω ω ω ω ω= + = +i j i j! !
Velocity and acceleration of the mass center C of the disk:
( )/ 2 2 2C C A b c c bω ω ω= × = × + = −v r j i k i kΩ
( ) ( )2 22 / 2 2 2 2 2C C A C c b b cω ω ω ω ω ω= × + × = − + −a j r j v i k! ! !
eff : Resolve into components.x z CA A mΣ = Σ + =F F i k a
( ) ( )2 22 2 2 2 x zA m c b A m b cω ω ω ω= − = − +! !
( )/A A C C A C C Cm b c mΣ = = + × = + + ×M H H r a H i k a! ! !
2 2 2 22 1 2
1 1 Resolve into components.2 4
mr m r b cω ω ω = + + +
i j!
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( ) ( )2 2 2 22 1 0 2
1 1 2 4A Ax yM mr M M m r b cω ω ω = = = + +
!
Since the couple 0M is given as constant, 2ω! is constant.
222
2.4 0.8 rad/s3t
ωω = = =!
(a) ( )2 2 2
080 1 10 16 12 0.8
32.2 4 12 12 12M
= + +
( )0 5.87 lb ft= ⋅M j!
(b) ( ) ( )280 12 160.8 2.4 17.09 lb32.2 12 12xA = − = −
( ) ( )280 16 120.8 2.4 16.96 lb32.2 12 12zA = − + = −
( ) ( )17.09 lb 16.96 lbA = − −R i k!
( ) ( )( )21 80 10 2.4 80 165.6 lb ft
2 32.2 12A xM = = ⋅
( )165.6 lb ftA = ⋅M i!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 103.
Angular velocity of shaft DCE and arm CBA: 2ω= kΩΩΩΩ
Angular velocity of disk A: 1 2ω ω= +j kωωωω
Its angular momentum about A: 1 2A x x y y z z y zI I I I Iω ω ω ω ω= + + = +H i j k j k
Let the reference frame Cxyz be rotating with angular velocity .ΩΩΩΩ
( ) ( )1 2 2 1 2A A A y z y zAxyzI I I Iω ω ω ω ω= + × = + + × +H H H j k k j k& & & &ΩΩΩΩ
2 2 22 1 1 2 2 1 1 2
1 1 1
2 2 4y y zI I I mr mr mrω ω ω ω ω ω ω ω= − + + = − + +i j k i j k& & & &
Velocity and acceleration of the mass center A of the disk:
( )2 / 2 2 2A A C b c c bω ω ω= × = × − = +v k r k i j i jωωωω
( ) ( )2 22 / 2 2 2 2 2A A C A c b b cω ω ω ω ω ω= × + × = − + +a k r k v i j& & &
effΣ = ΣF F
x y x y AD D E E m+ + + =i j i j a
Resolve into components.
( )22 2x xD E m c bω ω+ = −&
( )22 2y yD E m b cω ω+ = +&
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( )/E E A A E A A Am b c l mΣ = = + × = + − + ×M H H r a H i j k a& & &
( ) ( ) ( ) ( )2 2 2 20 2 2 2 2 22 x y Al D D M m bl cl m cl bl m b cω ω ω ω ω× + + = + − + + + +k i j k H i j k& & & &
2 20 2 1 2 2
12 2
2y xlD lD M m r bl clω ω ω ω − + + = − + −
i j k i&
2 2 2 2 21 2 2 2
1 1
2 4m r cl bl m r b cω ω ω ω + + − + + +
j k& & &
2 2 20 2
1:
4M m r b c ω = + +
k &
2 2 2 21 2 2 1 2 2
1 1:
2 2 2 2x xm m
D r cl bl E r cl bll l
ω ω ω ω ω ω = + − = − + −
j & & & &
2 2 2 22 1 2 2 2 1 2 2
1 1:
2 2 2 2y ym m
D r bl cl E r bl cll l
ω ω ω ω ω ω ω ω = + + = − + +
i & &
Data: 2.5 kg, 0.1 m,m r= =
0.15 m, 0.075 m, 0.18 mb c l= = =
21 1 2 250 rad/s, 15 rad/s , 12 rad/s, 0ω ω ω ω= = − = =& &
( )( ) ( ) ( ) ( )( )( )2 22.5 10.1 15 0 0.15 0.18 12 27.52 N
2 0.18 2xD = − + − = −
( )( ) ( ) ( )( ) ( )( )( )2 22.5 10.1 12 50 0 0.075 0.18 12 34.33 N
2 0.18 2yD = + + =
( ) ( )27.5 N 34.3 N= − +D i j!
( )( ) ( ) ( ) ( )( )( )2 22.5 10.1 15 0 0.15 0.18 12 26.48 N
2 0.18 2xE = − − + − = −
( )( ) ( ) ( )( ) ( )( )( )2 22.5 10.1 12 50 0 0.075 0.18 12 7.333 N
2 0.18 2yE = − + + = −
( ) ( )26.5 N 7.33 N= − −E i j!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 104.
Angular velocity of shaft DCE and arm CBA: 2ω= kΩ
Angular velocity of disk A: 1 2ω ω= +j kω
Its angular momentum about A: 1 2A x x y y z z y zI I I I Iω ω ω ω ω= + + = +H i j k j k
Let the reference frame Cxyz be rotating with angular velocity .Ω
( ) ( )1 2 2 1 2A A A y z y zAxyzI I I Iω ω ω ω ω= + × = + + × +H H H j k k j k! ! ! !Ω
2 2 22 1 1 2 2 1 1 2
1 1 12 2 4y y zI I I mr mr mrω ω ω ω ω ω ω ω= − + + = − + +i j k i j k! ! ! !
Velocity and acceleration of the mass center A of the disk:
( )2 / 2 2 2A A C b c c bω ω ω= × = × − = +v k r k i j i jω
( ) ( )2 22 / 2 2 2 2 2A A C A c b b cω ω ω ω ω ω= × + × = − + +a k r k v i j! ! !
effΣ = ΣF F
x y x y AD D E E m+ + + =i j i j a
Resolve into components.
( )22 2x xD E m c bω ω+ = −!
( )22 2y yD E m b cω ω+ = +!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
( )/E E A A E A A Am b c l mΣ = = + × = + − + ×M H H r a H i j k a! ! !
( ) ( ) ( ) ( )2 2 2 20 2 2 2 2 22 x y Al D D M m bl cl m cl bl m b cω ω ω ω ω× + + = + − + + + +k i j k H i j k! ! ! !
2 20 2 1 2 2
12 22y xlD lD M m r bl clω ω ω ω − + + = − + −
i j k i!
2 2 2 2 21 2 2 2
1 12 4
m r cl bl m r b cω ω ω ω + + − + + +
j k! ! !
2 2 20 2
1: 4
M m r b c ω = + +
k !
2 2 2 21 2 2 1 2 2
1 1: 2 2 2 2x xm mD r cl bl E r cl bll l
ω ω ω ω ω ω = + − = − + −
j ! ! ! !
2 2 2 22 1 2 2 2 1 2 2
1 1: 2 2 2 2y ym mD r bl cl E r bl cll l
ω ω ω ω ω ω ω ω = + + = − + +
i ! !
Data: 2.5 kg, 0.1 m,m r= =
0.15 m, 0.075 m, 0.18 mb c l= = =
21 1 2 2 250 rad/s, 0, 12 rad/s, 8 rad/sω ω ω ω α= = = = =! !
(a) ( ) ( ) ( ) ( ) ( )2 2 20
12.5 0.1 0.15 0.075 84
M = + + ( )0 0.613 N m= ⋅M k"
(b) ( )( ) ( )( )( ) ( )( )( )22.5 0 0.075 0.18 8 0.15 0.18 12 26.25 N2 0.18xD = + − = −
( )( ) ( ) ( )( ) ( )( )( ) ( )( )( )2 22.5 1 0.1 12 50 0.15 0.18 8 0.075 0.18 12 35.83 N2 0.18 2yD = + + =
( ) ( )26.3 N 35.8 N= − +D i j"
( )( ) ( )( )( ) ( )( )( )22.5 0 0.075 0.18 8 0.15 0.18 12 26.25 N2 0.18xE = − + − = −
( )( ) ( ) ( )( ) ( )( )( ) ( )( )( )2 22.5 1 0.1 12 50 0.15 0.18 8 0.075 0.18 12 5.833 N2 0.18 2yE = − + + = −
"
( ) ( )26.3 N 5.83 N= − −E i j"
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 105.
Use principal axes x, y, z with origin at O.
Angular velocity: ( )sin cosφ θ ψ φ θ= + +i k& &&ωωωω
sin , 0, cosx y zω φ θ ω ω ψ φ θ= = = +& &&
Angular momentum about O:
sinO x x y y z z zI I I I Iω ω ω φ θ ω′= + + = +H i j k i k&
Let the reference frame Oxyz be rotating with angular velocity sin cos .φ θ φ θ= +i k& &ΩΩΩΩ
O Ο= ×H H& ΩΩΩΩ
( ) ( )sin cos sin zI Iφ θ φ θ φ θ ω′= + × +i k k& & &
( )sin cos sinzI Iφ θ θ ω θ φ′= − j& &
O OΣ =M H&
( )sin sin cos sinzWc I Iθ φ θ θ ω θ′− = −j j&
( )coszWc I Iω φ θ φ′= − & &
( ) cosWc I I Iψ φ θ φ ′= − − & && (1)
Data: 3
lb 0.1875 lb16
W = =
3 20.18755.823 10 lb s ft
32.2m −= = × ⋅ ⋅
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( )2
2 3 6 21.055.823 10 44.582 10 lb s ft
12zI mk − − = = × = × ⋅ ⋅
( )2
2 3 6 22.255.823 10 204.715 10 lb s ft
12xI mk − − ′ = = × = × ⋅ ⋅
1.875 in. 0.15625 ft, 1800 rpm 188.496 rad/s,c ψ= = = =&
30 .θ = °
Substituting into (1),
( ) ( ) ( ) ( )60.1875 0.15625 44.582 10 188.496−= ×
( )6160.133 10 cos30φ φ− − × °& &
6 2 3 3138.679 10 8.4035 10 29.297 10 0φ φ− − −× − × + × =& &
30.298 26.584 3.714 rad/s, 56.882 rad/sφ φ= ± =& &
35.5 rpm, 543 rpmφ =& !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 106.
Use principal axes x, y, z with origin at O.
Angular velocity: ( )sin cosφ θ ψ φ θ= + +i k! !!ω
sin , 0, cosx y zω φ θ ω ω ψ φ θ= = = +! !!
Angular momentum about O:
sinO x x y y z z zI I I I Iω ω ω φ θ ω′= + + = +H i j k i k!
Let the reference frame Oxyz be rotating with angular velocity sin cos .φ θ φ θ= +i k! !Ω
O Ο= ×H H! Ω
( ) ( )sin cos sin zI Iφ θ φ θ φ θ ω′= + × +i k k! ! !
( )sin cos sinzI Iφ θ θ ω θ φ′= − j! !
O OΣ =M H!
( )sin sin cos sinzWc I Iθ φ θ θ ω θ′− = −j j!
(a) ( )coszWc I Iω φ θ φ′= − ! !!
( ) cosWc I I Iψ φ θ φ ′= − − ! !! (1)
(b) For Wc Iφ ψ ψφ≈! !! !" (2) !
(c) Data: 3 lb 0.1875 lb16
W = =
3 20.1875 5.823 10 lb s ft32.2
m −= = × ⋅ ⋅
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
( )2
2 3 6 21.055.823 10 44.582 10 lb s ft12zI mk − − = = × = × ⋅ ⋅
( )2
2 3 6 22.255.823 10 204.715 10 lb s ft12xI mk − − ′ = = × = × ⋅ ⋅
1.875 in. 0.15625 ft, 1800 rpm 188.496 rad/s,c ψ= = = =!
30 .θ = °
Substituting into (1),
( ) ( ) ( ) ( )60.1875 0.15625 44.582 10 188.496−= ×
( )6160.133 10 cos30φ φ− − × °! !
6 2 3 3138.679 10 8.4035 10 29.297 10 0φ φ− − −× − × + × =! !
30.298 26.584 3.714 rad/s, 56.882 rad/sφ φ= ± =! !
From (2), ( )( )( )( )6
0.1875 0.156253.486 rad/s
44.582 10 188.496WcI
φψ −
= = =×
!!
3.486 3.714% error 100%3.714
−= × % error 6.14%= − !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 107.
Use principal axes x, y, z with origin at A.
Angular velocity: ( )sin cosφ β ψ φ β= + −i k! !!ω
sin , 0, cosx y zω φ β ω ω ψ φ β= = = −! !!
Angular momentum about A:
A x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI Iφ β ψ φ β′= + −i k! !!
Let the reference frame Axyz be rotating with angular velocity sin cos .φ β φ β= −i k! !Ω
A Α= ×H H! Ω
( )sin sin cosI I Iφ ψ β φ β β ′= − + − j! !!
A AΣ =M H!
( )sin sin sin cosmgc I I Iβ φ ψ β φ β β ′− = − + − j j! !!
( ) 2 cosmgc I I Iφψ φ β′= + −! !!
( ) 2 cos1 0
I IImgc mgc
φ βφψ ′ −+ − =
!! ! (1)
Data: 3 in. 0.25 ft, 24 in. 2 ft,r c= = = =
232.2 ft/sg =
continued
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
( )22 21 0.25 0.03125 ft2 2
I rm
1= = =
( ) ( )2 22 2 21 1 0.25 2 4.015625 ft4 4
I r cm′
= + = + =
60 , 36 rpm 3.7699 rad/sβ φ= ° = =!
Substituting into (1),
( )( )( )( )
( )( )( )( )
20.03125 3.7699 4.015625 0.03125 3.7699 cos601 0
32.2 2 32.2 2ψ − °
+ − =!
31.82934 10 0.43965 1 0ψ−× + − =!
306.3 rad/s,ψ =! 2930 rpmψ =! !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 108.
Use principal axes x, y, z with origin at A.
Angular velocity: ( )sin cosφ β ψ φ β= + −i k! !!ω
sin , 0, cosx y zω φ β ω ω ψ φ β= = = −! !!
Angular momentum about A:
A x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI Iφ β ψ φ β′= + −i k! !!
Let the reference frame Axyz be rotating with angular velocity sin cos .φ β φ β= −i k! !Ω
A Α= ×H H! Ω
( )sin sin cosI I Iφ ψ β φ β β ′= − + − j! !!
A AΣ =M H!
( )sin sin sin cosmgc I I Iβ φ ψ β φ β β ′− = − + − j j! !!
( ) 2 cosmgc I I Iφψ φ β′= + −! !!
( ) 2 cos1 0
I IImgc mgc
φ βφψ ′ −+ − =
!! ! (1)
Data: 3 in. 0.25 ft, 24 in. 2 ft,= = = =r c
232.2 ft/sg =
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
( )22 21 0.25 0.03125 ft2 2
I rm
1= = =
( ) ( )2 22 2 21 1 0.25 2 4.015625 ft4 4
I r cm′
= + = + =
45 , 2100 rpm 219.91 rad/sβ ψ= ° = =!
Substituting into (1),
( )( )( )( )
( )( )( )
20.03125 219.91 4.015625 0.03125 cos 451 0
32.2 2 32.2 2φ φ− °
+ − =! !
( ) 20.106711 0.043748 1 0φ φ+ − =! !
6.1537 rad/s or 3.7145 rad/sφ φ= − =! !
58.8 rpm, 35.5 rpmφ = −! !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 109.
Use principal axes xyz with origin at A as shown.
For the solid cone, 0.080 m,r =
0.240 m,h = 3 0.180 m4hc = =
23
10I mr=
2 23 15 4
I m h r ′ = +
2 23 15 4
I I m h r ′− = −
Angular velocity. spin: ψ! about negative z axis
precession: φ! about positive z axis
φ ψ= −K k! !ω
( )cos sinφ β β ψ= + −k j k! !
0, sin , cosx y zω ω φ β ω φ β ψ= = = −! ! !
Angular momentum about fixed point A.
A x y zI I Iω ω ω′ ′= + +H i j k
( )sin cosI Iφ β φ β ψ′= + −j k! ! !
Let frame Axyz be rotating with angular velocity Ω .
cos sinφ φ β φ β= = +K j k! ! !Ω Rate of change of .AH
( )
0 sin cos
0 sin cosA A
I I
φ β φ β
φ β φ β ψ
= × =
′ −
i j kH H ! !!
! ! !
Ω
( ) 2 cos sin sinI I Iφ β β φψ β ′= − − + i! ! !
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Momentum about A. sin β= −A mgcM i
A A=M H! leads to
2 cosI I Igcm m
φ β φψ′ −= +! ! !
2 2 2 23 1 3cos5 4 10
h r rφ β φψ = − +
! ! !
( )2 2 2 220 12 3 cos 6gc h r rφ β φψ= − +! ! !
( )2
2 2 220 6cos12 3
gc rh r
φψβφ
−=−
! !!
Data: 1600 rpm = 167.552 rad/sψ =!
40 rpm = 4.1888 rad/sφ =!
( )( )( ) ( )( ) ( )( )( )( ) ( )( ) ( )
2
2 2 2
20 9.81 0.180 6 0.080 167.552 4.1888cos
12 0.240 3 0.080 4.1888β
−=
−
0.70947= 44.8β = ° !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 110.
Use principal axes xyz with origin at A as shown.
For the solid cone, 0.080 m,r =
0.240 m,h = 3 0.180 m4hc = =
23
10I mr=
2 23 15 4
I m h r ′ = +
2 23 15 4
I I m h r ′− = −
Angular velocity. spin: ψ! about negative z axis
precession: φ! about positive z axis
φ ψ= −K k! !ω
( )cos sinφ β β ψ= + −k j k! !
0, sin , cosx y zω ω φ β ω φ β ψ= = = −! ! !
Angular momentum about fixed point A.
A x y zI I Iω ω ω′ ′= + +H i j k
( )sin cosI Iφ β φ β ψ′= + −j k! ! !
Let frame Axyz be rotating with angular velocity Ω .
cos sinφ φ β φ β= = +K j k! ! !Ω
Rate of change of .AH
( )
0 sin cos
0 sin cosA A
I I
φ β φ β
φ β φ β ψ
= × =
′ −
i j kH H ! !!
! ! !
Ω
( ) 2 cos sin sinI I Iφ β β φψ β ′= − − + i! ! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Momentum about A. sin β= −A mgcM i
A A=M H! leads to
2 cosI I Igcm m
φ β φψ′ −= +! ! !
2 2 2 23 1 3cos5 4 10
h r rφ β φψ = − +
! ! !
( )2 2 2 220 12 3 cos 6gc h r rφ β φψ= − +! ! !
( )2 2 2
2
20 12 3 cos
6
gc h r
r
φ βψ
φ
− −=
!! !
Data: 30β = °
30 rpm = rad/sφ π=!
( )( )( ) ( )( ) ( )( )
( )( )
2 2 2
2
20 9.81 0.180 12 0.240 3 0.080 cos30
6 0.080
πψ
π
− − ° =!
245.13 rad/s= 2340 rpmψ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 111.
Choose principal centroidal axes xyz as shown.
The symmetry (spin) axis is the z axis.
Reduce the drag force to a force-couple system at the mass center.
( ) ( )sin cos cos sinD W D Wβ β β β= − − −F i k
sinG Dc β=M j
For the occurrence of steady precession, the precession axis must be parallel to the drag force. Thus, 3 .θ β= = °
(a) Using Equation (18.44), G GΣ =M H!
( )sin cos sinzDc I Iβ ω φ θ φ θ′= − ! !
Using and coszβ θ ω ψ φ θ= = + !! gives
( ) 2 cosI I I Dcψφ φ θ′− − =! !! (1)
Neglecting the quadratic term in ,φ!
DcI DcI
ψφ φψ
≈ ≈! !!!
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Data: 18 kgm =
( )( )22 218 0.06 0.0648 kg mzI mk= = = ⋅
6000 rpm 628.32 rad/s, 0.175 mcψ = = =!
( )( )( )( )
110 0.1750.4728 rad/s
0.0648 628.32φ ≈ =! 4.51 rpmφ ≈! !
(b) ( )( )22 218 0.25 1.125 kg mxI mk′ = = = ⋅
21.0602 kg mI I′ − = ⋅
Substituting into Equation (1),
( )( ) ( ) ( )( )20.0648 628.32 1.0602 cos3 110 0.175φ φ− ° =! !
21.0587 40.7151 19.25 0φ φ− + =! !
19.2288 18.7501 0.4787 rad/s, or 37.98 rad/sφ = ± =!
4.57 rpm, 363 rpmφ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 112.
Use principal centroidal axes x, y, z as shown.
Angular velocity: ( )sin cosφ θ ψ φ θ= − + +i k! !!ω
Angular momentum about the mass center G:
G x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI Iφ θ ψ φ θ′= − + +i k! !!
Let the reference frame Gxyz be rotating with angular velocity
sin cosφ θ φ θ= − +i k! !Ω
G G= ×H H! Ω
( ) 2sin sin cosI I Iφψ θ φ θ θ ′= − − j! !!
Acceleration of the mass center:
( ) 2sin sinl cβ θ φ= +a !
eff :Σ = ΣF F
: cos 0, cosmgT mg Tβ
β− = = (1)
: sinT maβ =
( ) 2tan sin sing l cβ β θ φ= + ! (2)
continued
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: ( )sinG GM Tc Hβ θΣ = − = !
( ) ( ) 2sinsin sin cos
cosmgc
I I Iβ θ
ψφ θ φ θ θβ
−′= − −! !!
For alignment of axis BC with cord AB, .θ β=
Substituting into (3),
0 cosI I Im m
ψ φ β′ −= − !! ( )cos II I
ψβφ
=′−!!
For a cone, 34
c h= 2 23 310 40
I mr md= =
2 2 2 2 23 3 3 320 5 80 80
I mr mh mc md mh′ = + − = −
2 23 380 80
I I md mh′ − = +
2
2 22I I d
I d h′ − =
+
( )2
2 22cos d
d hψβ
φ=
+
!! ( )
21
2 22cos d
d hψβ
φ− = +
!! "
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 113.
Use principal centroidal axes x, y, z as shown.
Angular velocity: ( )sin cosφ θ ψ φ θ= − + +i k! !!ω
Angular momentum about the mass center G:
G x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI Iφ θ ψ φ θ′= − + +i k! !!
Let the reference frame Gxyz be rotating with angular velocity
sin cosφ θ φ θ= − +i k! !Ω
G G= ×H H! Ω
( ) 2sin sin cosI I Iφψ θ φ θ θ ′= − − j! !!
Acceleration of the mass center:
( ) 2sin sinl cβ θ φ= +a !
eff :Σ = ΣF F
: cos 0, cosmgT mg Tβ
β− = = (1)
: sinT maβ =
( ) 2tan sin sing l cβ β θ φ= + ! (2)
: ( )sinG GM Tc Hβ θΣ = − = !
( ) ( ) 2sinsin sin cos
cosmgc
I I Iβ θ
ψφ θ φ θ θβ
−′= − −! !! (3)
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Data: 3 in. 0.25 ft, 12 in. 1 ft,r h= = = =
23 0.75 ft, 32.2 ft/s4
c h g= = =
( )22 23 3 0.25 0.01875 ft10 10
I rm
= = =
( ) ( ) ( )2 2 22 2 23 3 3 30.25 1 0.7520 5 20 5
I r h cm′
= + − = + −
20.046875 ft=
20.028125 ftI Im
′ − =
45 , 30 15β θ β θ= ° = ° − = °
(a) Dividing Eq. (3) by m and substituting numerical data,
( )( ) ( )( ) ( )( )232.2 0.75 sin150.01875 8 sin 30 0.028125 8 sin 30 cos30
cos 45ψ
°= ° − ° °
°!
8.8395 0.075 0.77942ψ= −!
128.252 rad/sψ =! 128.3 rad/sψ =! !
(b) Substituting data into Eq. (2),
( )( )232.2 tan 45 sin 45 0.75sin 30 8l° = ° + °
32.2 45.255 24, 0.1812 ftl l= + =
2.17 in.l = !
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Chapter 18, Solution 114.
( )( )( )( ) 925800 years 25800 yr 365.24 day/yr 24 h/day 3600 s/h 814.16 10 s= = ×
129
27.7173 10 rad/s
814.16 10
πφ −= = ××
&
( )( )62
72.935 10 rad/s23.93 h 3600 s/h
πψ −= = ×&
mass density of Earth: 2 434410.6832 lb s /ft
32.2g
γρ = = = ⋅
radius of Earth: ( )( ) 63960 mi 5280 ft/mi 20.9088 10 ftR = = ×
mass of Earth: ( ) ( )33 6 21 24 420.9088 10 10.6832 409.05 10 lb s /ft
3 3Rπ ρ π= × = × ⋅
( )( )22 21 6 36 22 2409.05 10 20.9088 10 71.531 10 lb s ft
5 5I mR= = × × = × ⋅ ⋅
Using Equation (18.44),
( )cos sinzM I Iω φ θ φ θ′= − & &
( ) cos sinI I Iψ φ θ φ θ ′= + − & &&
sinIψφ θ= &&
( )( )( )36 6 1271.531 10 72.935 10 7.7173 10 sin 23.45− −= × × × °
2116.02 10 lb ft= × ⋅
2116.02 10 lb ftM = × ⋅ !
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Chapter 18, Solution 115.
Use principal centroidal axes x, y, z as shown.
Angular velocity: ( )sin cosφ θ ψ φ θ= − + +i k! !!ω
Angular momentum about the mass center G:
G x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI Iφ θ ψ φ θ′= − + +i k! !!
Let the reference frame Gxyz be rotating with angular velocity
sin cosφ θ φ θ= − +i k! !Ω
G G= ×H H! Ω
( ) 2sin sin cosI I Iφψ θ φ θ θ ′= − − j! !!
Acceleration of the mass center:
( ) 2sin sinl cβ θ φ= +a !
eff :Σ = ΣF F
: cos 0, cosmgT mg Tβ
β− = = (1)
: sinT maβ =
( ) 2tan sin sing l cβ β θ φ= + ! (2)
: ( )sinG GM Tc Hβ θΣ = − = !
( ) ( ) 2sinsin sin cos
cosmgc
I I Iβ θ
ψφ θ φ θ θβ
−′= − −! !! (3)
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For a solid sphere, 22 ,5
I I mc′= = 0I I′− =
Substituting into Eg. (3),
( ) 2cos sin sin cos 2 sincos 5
mgcmc
θ β θ βψφ θ
β−
= !!
( ) 22tan tan tan5
mgc mcβ θ ψφ θ− = !!
5 tantan5 2
gg c
βθψφ
=+ !!
1 5 tantan5 2
gg c
βθψφ
− = + !!
!
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 116.
Use principal centroidal axes x, y, z as shown.
Angular velocity: ( )sin cosφ θ ψ φ θ= − + +i k! !!ω
Angular momentum about the mass center G:
G x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI Iφ θ ψ φ θ′= − + +i k! !!
Let the reference frame Gxyz be rotating with angular velocity
sin cosφ θ φ θ= − +i k! !Ω
G G= ×H H! Ω
( ) 2sin sin cosI I Iφψ θ φ θ θ ′= − − j! !!
Acceleration of the mass center:
( ) 2sin sinl cβ θ φ= +a !
eff :Σ = ΣF F
: cos 0, cosmgT mg Tβ
β− = = (1)
: sinT maβ =
( ) 2tan sin sing l cβ β θ φ= + ! (2)
: ( )sinG GM Tc Hβ θΣ = − = !
( ) ( ) 2sinsin sin cos
cosmgc
I I Iβ θ
ψφ θ φ θ θβ
−′= − −! !! (3)
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For a solid sphere, 22 ,5
I I mc′= = 0I I′− =
Substituting into Eg. (3),
( ) 2cos sin sin cos 2 sincos 5
mgcmc
θ β θ βψφ θ
β−
= !!
( ) 22tan tan tan5
mgc mcβ θ ψφ θ− = !!
5 tantan5 2
gg c
βθψφ
=+ !!
1 5 tantan5 2
gg c
βθψφ
− = + !!
Data: 40 mm = 0.040 m, = 9.81 m/sc g=
5 rad/s, = 30φ β= °!
(a) 0:ψ =! ( )( )( )( )
1 5 9.81 tan 30tan
5 9.81θ − °
=
30.0θ = ° !
(b) 30 rad/s:ψ =! ( )( )( )( ) ( )( )( )( )
1 5 9.81 tan 30tan
5 9.81 2 0.040 30 5θ − °
= +
24.9θ = ° !
(c) 30 rad/s:ψ = −! ( )( )( )( ) ( )( )( )( )
1 5 9.81 tan 30tan
5 9.81 2 0.04 30 5θ − °
= + −
37.4θ = ° !
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Chapter 18, Solution 117.
By Equation (18.48), sin cos
, 0, G Gx y z
H H
I I
θ θω ω ω= − = =′
By Equation (18.35) with 0,θ =&
sin , 0, cosx y zω φ θ ω ω ψ φ θ= − = = +& &&
Eliminating , and x zω ω
GH
Iφ =
′&
coscos GH
I
θψ φ θ+ =&&
( )coscos cos coscos GG G G H I IH H H
I I I II
θθ θ θψ φ θ′ −
= − = − =′ ′
&&
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 118.
(a) Angular velocity of the body: 2sinφ θ ω= − +i k!ω
Its angular momentum about G: 2sinG I Iφ θ ω′= − +H i k!
Let the reference frame Gxyz be rotating with angular velocity ,Ω where
sin cosφ θ φ θ= − +i k! !Ω
( ) ( ) ( )20 sin cos sinG G GGxyzI Iφ θ φ θ φ θ ω′= + × = + − + × − +H H H i k i k! ! !! ! Ω
22 sin sin cosI Iφω θ φ θ θ′= −! !
For no force, 0G =H!
Hence, ( )2 2cos sin 0 or cos 0I I I Iω φ θ φ θ ω φ θ′ ′− = − =! ! ! (1)
Solving for ,φ! 2
cosI
Iωφ
θ=
′!
(b) Comparing Equation (1) with Equation (18.44) yields 0 0,Σ =M which is the condition for no force.
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Chapter 18, Solution 119.
Angular velocity of the body: ( )sin cosφ θ φ θ ψ= − + +i k& & &ωωωω
Let the reference frame Gxyz be rotating with angular velocity ,ΩΩΩΩ where
sin cosφ θ φ θ= − +i j& &ΩΩΩΩ
Angular acceleration of the body: Gxyz= + ×&α ω Ω ωα ω Ω ωα ω Ω ωα ω Ω ω
0 sinφψ θ= + j& &αααα
The rate of change of angular velocity as observed from the body is .−αααα
Assume that −αααα may be represented as the angular velocity vector rotating with angular velocity .l m n+ +i j k
( ) ( ) ( )x z z x z xl m n m n l mω ω ω ω ω ω− = + + × + = + − −i j k i k i j kαααα
Matching components: : 0 0zm mω= =i
: sin x zn lφψ θ ω ω− = −j & & (1)
: 0 0xm mω= − =k
From Equation (1), ( )sin sin cosn lφψ θ φ θ φ θ ψ− = − − +& & && &
from which 0 and .l n ψ= = &
Using Equation (18.44) with 0 0Σ =M yields cos 0zI Iω φ θ′− =&
or cos zI
I
ωφ θ =′
&
But, cos zz
I
I
ωω ψ φ θ ψ= + = +′
&& &
Solving for ,ψ& zI I
Iψ ω′ −=&
Using 2 and z nω ω ψ= = & yields 2.I I
nI
ω′ −=′
!
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Chapter 18, Solution 120.
For no force, 0G =M
(a) Using Equation (18.44), ( )0 cos sinzI Iω φ θ φ θ′= − ! !
cos 0zI Iω φ θ′− =!
Using coszω ψ φ θ= + !! yields ( ) cos 0I I Iψ φ θ′− − =!!
( )cosI
I Iψφ
θ=
′ −!!
( ) secII I
ψφ θ=′−!!
For a flat disk, 12
I I′ =
For any other shape, 12
I I′ >
Hence, 1 and 22
II I II I
′− < >′−
Also sec 1.θ > 2φ ψ>! !
(b) 1tan tan or tan tan tan2
I II I
γ θ θ γ γ′= = >
′
Angle of surface of space cone is .γ θ−
Angle of axis is .θ
( ) ( )( )
tan tan1 1tan tan2 2 1 tan tan
θ γ θθ θ γ θ
θ γ θ+ −
> + − = + −
( ) ( )1 11 tan tan tan tan tan2 2
θ γ θ θ θ γ θ + − > + −
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( ) ( )2 1 1tan tan tan tan tan2 2
θ θ γ θ θ γ θ+ − > + −
( ) ( )21 1tan tan tan tan2 2
θ γ θ θ γ θ> − − −
( )1 1tan tan2 2
θ γ θ> −
( )tan tanθ γ θ> −
( )θ γ θ> −
The axis lies outside the space cone.
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Chapter 18, Solution 121.
Angular velocity of the body: ( )sin cosφ θ φ θ ψ= − + +i k& & &ωωωω
Let the reference frame Gxyz be rotating with angular velocity ΩΩΩΩ, where
sin cosφ θ φ θ= − +i j& &ΩΩΩΩ
Angular acceleration of the body: ω= + ×&Gxyzα Ω ωα Ω ωα Ω ωα Ω ω
The rate of change of angular velocity as observed from the body is −αααα
Assume that α− may be represented as the angular velocity vector rotating with angular velocity
.+ +i j kl m n
( ) ( ) ( )ω ω ω ω ω ω− = + + × + = − + − −i j k i k i j kx z z x z xl m n m n l mαααα
Matching components: : 0 0zm mω= =i
: sin x zn lφψ θ ω ω− = −j & & (1)
: 0 0xm mω= − =k
From Equation (1), ( )sin sin cosn lφψ θ φ θ φ θ ψ− = − − +& & &&
from which 0 and .ψ= = &l n
Using Equation (18.44) with 0 0 yields cos 0zI Iω φ θ′Σ = − =M &
or cos zI
I
ωφ θ =′
&
But, cos zz
I
I
ωω ψ φ θ ψ= + = +′
&& &
Solving for ,ψ& ψ ω′ −=& zI I
I
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Using 2 2 and yields ω ω ψ ω′ −= = =′
&zI I
n nI
Data for Earth: 0.9967 , 0.0033 ,′ ′= − = −I I I I I
2 20.0033
0.0033110.9967
ω ω= − = −n
( )( )2 2
2 1 2 2period 302.03 302.03 24 h 7248 h
0.003311
π π πω ω
= = = = =n
period 302 days= !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 122.
tan ωγω
= − x
z
15γ = °
For steady precession with no force,
tan tan 3tan15θ γ′= = °I
I
38.794θ = °
(a) 38.794 15β θ γ= − = − °
23.8β = °!
(b) sin sinxω φ θ ω γ= − = −!
( )( )
200 rpm sin15sinsin sin 38.794
ω γφθ
°= =
°!
82.621 rpm=
precession: 82.6 rpmφ =! !
cos coszω ψ φ θ ω γ= + =!!
cos cos 200cos15 82.621cos38.794ψ ω γ φ θ= − = ° − °!!
spin: 128.8 rpmψ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 123.
Moments of inertia: 2 21 1, 2 4
I mr I mr′= =
Euler angle θ for steady precession: 15θ = °
For axisymmetric body under no force, Equation (18.49) gives for the body cone angle:
tan tan 2 tan15 28.187γ θ γ= = ° = °′
II
(a) Angular velocity ( )sin cosω γ γ= − +i kω
Its projection onto the vertical direction is
( ) ( )cos sin cos sin cosω β ω γ γ θ θ= ⋅ = − + ⋅ − +k i k i kω
( ) ( )sin sin cos cos cosω γ θ γ θ ω γ θ= + = −
( )cos cos 28.187 15 13.187β γ θ β γ θ= − = − = ° − ° = °
Angle between ω and vertical direction GD: 13.19β = ° !
(b) sintancos
x
z
ω φ θγω φ θ ψ
= − =+
!! !
from which ( )sin sin 28.187 2.0705
sin sin13.187ψ γ ψφ ψ
θ γ°= = = −
− − °! !! !
With ( )( )600 rpm, 2.0705 600ψ φ= = −!! 1242 rpmφ =! (retrograde)!
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Chapter 18, Solution 124.
Mass of satellite: 2800 24.845 lb s /ft32.2
Wmg
= = = ⋅
Principal moments of inertia: ( )2
2 228.824.845 143.106 lb s ft12x xI mk = = = ⋅ ⋅
( )2
2 232.424.845 181.118 lb s ft12y yI mk = = = ⋅ ⋅
2143.106 lb s ftz xI I= = ⋅ ⋅
Mass of meteorite: ( ) ( )26 0.011649 lb s /ft
16 32.2m = = ⋅′
Initial momentum of meteorite: ( ) ( )0 0.011649 1600 1300 4000m = − + +′v i j k
( ) ( ) ( )18.633 lb s 15.140 lb s 46.584 lb s= − ⋅ + ⋅ + ⋅i j k
Assume that the position of the mass center of the satellite plus the meteorite is essentially that of the satellite alone. Position of point B relative to the mass center.
( ) ( )/42 20 3.5 ft 1.66667 ft12 12B G = − = −
r i j i j
Angular velocity of satellite before impact. ( )0 1.5 rad/s= jω ( ) ( ) ( )0 0 00, 1.5 rad/sx z yω ω ω= = =
Angular momentum of satellite-meteorite system before impact. ( ) ( )0 / 00G y B GI mω= + × ′H j r v
( ) ( )
( ) ( ) ( )
181.118 1.5 3.5 1.66667 018.633 15.140 46.584
77.64 lb s ft 108.637 lb s ft 21.935 lb s ft
= + −−
= − ⋅ ⋅ + ⋅ ⋅ + ⋅ ⋅
i j kj
i j k
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Principle of impulse and momentum for satellite-meteorite system. Moments about G:
( ) ( )1 0G G G= =H H H
Angular velocity immediately after impact. x y zω ω ω= + +i j kω
Neglect the mass of the meteorite.
G x x y y z zI I Iω ω ω= + +H i j k
( ) 77.64 0.54253 rad/s
143.106G x
xx
HI
ω −= = = −
( ) 108.637 0.59981 rad/s
181.118G y
yy
H
Iω = = =
( ) 21.934 0.15327 rad/s143.106
G zz
z
HI
ω = = =
( ) ( ) ( )0.54253 rad/s 0.59981 rad/s 0.15327 rad/s= − + +i j kω
( ) ( ) ( )2 2 20.54253 0.59981 0.15327 0.82317 rad/sω = + + =
( ) ( ) ( )2 2 277.64 108.637 21.935 135.319 lb s ftGH = + + = ⋅ ⋅
Motion after impact. Since the moments of inertia xI and zI are equal, the body moves as an axisymmetrical body with the y axis as the symmetry axis.
Moment of inertia about the symmetry axis: 2181.118 lb s ftyI I= = ⋅ ⋅
Moment of inertia about a transverse axis through G:
2143.106 lb s ftx zI I I= = = ⋅ ⋅′
The motion is a steady precession φ! about the precession axis together with a steady spin ψ! about the spin or symmetry axis. Since ,I I> ′ the precession is retrograde.
Precession axis. The precession axis is directed along the angular momentum vector HG, which remains fixed. Immediately after impact its direction cosines relative to the body axes x, y, z are:
( ) 77.64cos 0.57376
135.319G x
xG
HH
θ −= = = − 125.0xθ = ° !
( ) 108.637cos 0.80282
135.319G y
yG
H
Hθ = = = 36.6yθ = ° !
( ) 21.935cos 0.16210
135.319G z
zG
HH
θ = = = 80.7zθ = ° !
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The angle θ between the spin axis (y-axis) and the precession axis remains constant.
36.600yθ θ= = °
The angle γ between the angular velocity vector and the spin axis (y-axis) is
0.59981cos0.82317
yωγ
ω= = 43.226γ = °
The angle γ could also have been calculated from
181.118tan tan tan 36.600143.106
II
γ θ= = °′
The angle between the precession axis and the angular velocity vector is
6.626γ θ− = °
Rates of precession and spin.
Set up the triangle of vector addition for the components of angular velocity. Apply the law of sines.
( )sin sin sinω φ ψ
θ γ θ γ= =
−
! !
( )sin 0.82317 sin 6.626sin sin 36.600
ω γ θφ
θ− °= =
°!
( )0.1593 rad/s retrogradeφ =! !
sin 0.82317 sin 43.226sin sin 36.600
ω γψθ
°= =°
!
0.946 rad/sψ =! !
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Chapter 18, Solution 125.
Mass of satellite: 2800 24.845 lb s /ft32.2
wmg
= = = ⋅
Principal moments of inertia: ( )2
2 228.824.845 143.106 lb s ft12x xI mk = = ⋅ ⋅
( )2
2 232.424.845 181.118 lb s ft12y yI mk = = = ⋅ ⋅
2143.106 lb s ftz xI I= = ⋅ ⋅
Mass of meteorite: ( ) ( )26 0.011649 lb s /ft
16 32.2m = = ⋅′
Initial momentum of meteorite: ( ) ( )0 0.011649 1600 1300 4000m = − + +′v i j k
( ) ( ) ( )18.633 lb s 15.140 lb s 46.584 lb s= − ⋅ + ⋅ + ⋅i j k
Assume that the position of the mass center of the satellite plus the meteorite is essentially that of the satellite alone.
Position of point A relative to the mass center.
( )/42 3.5 ft12A G = =r i i
Angular velocity of satellite before impact. ( )0 1.5 rad/s= jω ( ) ( ) ( )0 0 00, 1.5 rad/sx z yω ω ω= = =
Angular momentum of satellite-meteorite system before impact. ( ) ( )0 / 00G y A GI mω= + × ′H j r v
( ) ( )
( ) ( )
181.118 1.5 3.5 0 018.633 15.140 46.584
108.637 lb s ft 52.99 lb s ft
= +−
= ⋅ ⋅ + ⋅ ⋅
i j kj
j k
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Principle of impulse and momentum for satellite-meteorite system. Moments about G:
( ) ( )1 0G G G= =H H H
Angular velocity immediately after impact. x y zω ω ω= + +ω i j k
Neglect the mass of the meteorite.
G x x y y z zI I Iω ω ω= + +H i j k
( )
0G xx
x
HI
ω = =
( ) 108.637 0.59981 rad/s
181.118G y
yy
H
Iω = = =
( ) 52.99 0.37028 rad/s
143.106G z
zz
HI
ω = = =
( ) ( )0.59981 rad/s 0.37028 rad/s= +j kω
( ) ( )2 20.59981 0.37028 0.70490 rad/sω = + =
( ) ( )2 2108.637 52.99 120.872 lb s ftGH = + = ⋅ ⋅
Motion after impact. Since the moments of inertia xI and zI are equal, the body moves as an axisymmetrical body with the y axis as the symmetry axis.
Moment of inertia about the symmetry axis: 2181.118 lb s ftyI I= = ⋅ ⋅
Moment of inertia about a transverse axis through G:
2143.106 lb s ftx zI I I= = = ⋅ ⋅′
The motion is a steady precession φ! about the precession axis together with a steady spin ψ! about the spin or symmetry axis. Since ,I I> ′ the precession is retrograde.
Precession axis. The precession axis is directed along the angular momentum vector HG, which remains fixed. Immediately after impact its direction cosines relative to the body axes x, y, z are:
( )
cos 0G xx
G
HH
θ = = 90.0xθ = ° !
( ) 108.637cos 0.89878
120.872G y
yG
H
Hθ = = = 26.0yθ = ° !
( ) 52.99cos 0.43840
120.872G z
zG
HH
θ = = = 64.0zθ = ° !
continued
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
The angle θ between the spin axis (y axis) and the precession axis remains constant.
26.002yθ θ= = °
The angle γ between the angular velocity vector and the spin axis (y axis) is
0.59981cos0.70490
yωγ
ω= = 31.689γ = °
The angle γ could also have been calculated from
181.118tan tan tan 26.002143.106
II
γ θ= = °′
The angle between the precession axis and the angular velocity vector is
5.687γ θ− = °
Rates of precession and spin.
Set up the triangle of vector addition for the components of angular velocity. Apply the law of sines.
( )sin sin sinω φ ψ
θ γ θ γ= =
−
! !
( )sin 0.70490 sin 5.687sin sin 26.002
ω γ θφ
θ− °= =
°!
( )0.1593 rad/s retrogradeφ =! !
sin 0.70490 sin 31.689sin sin 26.002
ω γψθ
°= =°
!
0.844 rad/sψ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 126.
For entire station: ( )2 2 21 13 ,
12 2I m a L I ma′ = + =
( )( )( )( ) ( )
22
2 2 2 2
6 360.0582524
3 3 3 30= = =
′ + +I a
I a L
From Equation (18.49), tan tan 0.0582524 tan 40 2.7984γ θ γ= = ° = °′
I
I
( )sin 2 rev/h sin 40 1.28557 rev/hxω φ θ= − = − ° = −&
1.28557
26.3005 rev/htan tan
ωωγ γ
= − = =xz
cos 26.3005 2cos 40zψ ω φ θ= − = − °&&
24.8 rev/hψ =& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 127.
(a) Angular velocity after impact
From Sample Problem 18.6:
2 21 5,
2 4′= = = = =z x yI I ma I I I ma
Conservation of angular momentum: Angular momentum after impact:
( )0 0 0 0 0 0G C m I a a m v Iω ω= × + = − − × +H r v k j k i k
( )0 0 0 0 0am v I am vω= − + +j k
Data: 0800 mm 0.8 m, 60 rpm 2 rad/s,ω π= = = =a
0 02000 m/s, 1000
= = mv m
( )0ω = =G x
xx
H
I
( )0 0 0 0
2
45 54
ω = = − = −G y
yy
H am v m v
I m ama
4 1 2000
2 rad/s5 1000 0.8 = − = −
( ) 0 0 0 00 0
22
12
ω ω ω= = + = +G zz
z
H am v m v
I m ama
1 2000
2 2 11.2832 rad/s1000 0.8
π = + =
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( ) ( )2.00 rad/s 11.28 rad/s= − +j kωωωω
( ) ( )2 22 11.2832 11.4591 rad/s 109.426 rpmω = + = =
109.4 rpω =
2tan 10.0515
11.2832
ωγ γ
ω= = = °y
z
90 , xγ γ= °
(b) Precession axis
( )5 2tan tan 2 23.900
4 11.2832θ γ θ′ = = = °
I
I
90 , xθ θ= °
(c) Rates of precession and spin
13.8484θ γ− = °
Law of sines
( )sin sin sin
φ ψ ωγ θ γ θ
= =−
& &
sin 109.4sin10.05
sin sin 23.9
ω γφθ
°= =°
&
precession: 47.1 rpmφ =& !
( )sin 109.4sin13.85
sin sin 23.9
ω θ γψ
θ− °= =
°&
spin: 64.6 rpmψ =& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 128.
Immediately after the rod breaks, the angular velocity remains equal to that calculated in Sample Prob.18.6.
6.594 rad/sω = tan 0.3183γ = 17.7γ = °
For disk A alone, 21 ,2
I ma= 214
I ma′ =
From Eq. (18.49) of textbook,
1tan tan tan 0.15915 9.042
II
θ γ γ θ′= = = = °
The new precession axis makes angleθ with the z-axis. Its direction angles are:
90 99.04xθ θ= + ° = ° !
90yθ = ° !
9.04zθ θ= = ° !
Since ,γ θ> the precession is retrograde.
The angular velocity vector is the sum of an angular velocityφk! along the precession axis plusψk! along the spin axis (z-axis). This vector addition is performed using a triangle construction and applying the law of sines.
( )sin sin sinω φ ψ
θ γ γ θ= =
−
! !
sin 6.594sin17.7 12.76 rad/ssin sin 9.04
ω γφθ
°= = =°
!
( )sin 6.594sin8.66 6.32 rad/ssin sin 9.04
ω γ θψ
θ− °= = =
°!
( )121.8 rpm retrogradeφ =! !
60.3 rpmψ =! !
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Chapter 18, Solution 129.
Place the origin at the center of mass and let Oxyz be a principal axis frame of reference with the y axis directed along the moving axle AB. Let the Z axis lie along the fixed axle. Useful unit vectors are i, j and k along the x, y, z axes and K along the Z axis.
sin cosθ θ= − +K i k
Angular velocity: φ θ= +ω k j! !
sin cosω φ θ θ φ θ= − + +i j k! ! !
Moments of inertia: 1 2, x y z yI e I I e I= =
Angular momentum about O.
O x x y y z zI I Iω ω ω= + +H i j k
( )1 2sin cosyI e eφ θ θ φ θ= − + +i j k! ! !
The moment about the fixed Z axis is zero, hence, constantO ⋅ =H K
( )2 21 2 1sin cosO y yI e e I Cθ θ φ⋅ = + =H K !
( )2 211 1 0 2 0 02 2
1 2 sin cos
sin cosC C e e
e eφ θ θ φ
θ θ= = +
+! !
Twice the kinetic energy: 2 2 22 constantx x y y z zT I I Iω ω ω= + + =
( ) ( )2 2 2 2 21 2 1 22 sin cosy y yT I e e I C I Cθ θ φ θ φ θ = + + = + =
! ! ! !
2 22 1 2 0 1 0 C C C Cθ φ θ φ= − = +! ! ! !
Data: 2 2 21 2 1 21, 2, sin cos 1 cose e e eθ θ θ= = + = +
0 0 090 , 0, 16 rad/sθ θ φ= ° = =! !
( )( )21
161 cos 90 16 16 rad/s 1 cos
C φθ
= + ° = =+
!
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(a) min16 8
1 cos0φ = =
+! min 8.00 rad/sφ =! !
( )( ) ( )22 0 16 16 256 rad/sC = + =
22 1C Cθ φ= −! !
(b) ( ) ( )( ) ( )22
2 1 minmax256 16 8 128 rad/sC Cθ φ= − = − =! ! max 11.31 rad/sθ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 130.
Place the origin at the center of mass and let Oxyz be a principal axis frame of reference with the y axis directed along the moving axle AB. Let the Z axis lie along the fixed axle. Useful unit vectors are i, j, and k along the x, y, z axes and K along the Z axis.
sin cosθ θ= − +K i k
Angular velocity: φ θ= +K j& &ωωωω
sin cosω φ θ θ φ θ= − + +i j k& & &
Moments of inertia: 1 2, x y z yI e I I e I= =
Angular momentum about O:
0 x x y y z zI I Iω ω ω= + +H i j k
( )1 2sin cosyI e eφ θ θ φ θ= − + +i j k& & &
The moment about the fixed Z axis is zero, hence constant.O ⋅ =H K
( )2 21 2 1sin cosO y yI e e I Cθ θ φ⋅ = + =H K &
( )2 211 1 0 2 0 02 2
1 2
sin cossin cos
CC e e
e eφ θ θ φ
θ θ= = +
+& &
Twice the kinetic energy: 2 2 22 constantx x y y z zT I I Iω ω ω= + + =
( )2 2 2 21 22 sin cosyT I e eθ θ φ θ = + +
& &
( )2 21 2y yI C I Cφ θ= + =& &
continued
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2 22 1 2 0 1 0 C C C Cθ φ θ φ= − = +& & & &
Data: 2 2 21 2 1 21, 2 sin cos 1 cosθ θ θ= = + = +e e e e
0 0 045 , 0, 8 rad/sθ θ φ= ° = =& &
( ) ( )21 0 2
1 121 cos 45 1 8 12 rad/s
2 1 cosC φ φ
θ = + ° = + = = +
& &
( )( ) ( )22 0 12 96 96 rad/s= + =C
(a) 22
14496 12 96 0
1 cosθ φ
θ= − = − ≥
+& &
2cos 0.5 cos 0.70711θ θ> >
45 45θ− ° < < °!
(b) min12
6 rad/s1 cos 0
φ = =+
&
min 6.00 rad/sφ =& !
(c) ( ) ( )( ) ( )2 2max 2 1 min 96 12 6 24 rad/sC Cθ φ= − = − =& &
max 4.90 rad/sθ =& !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 131.
Place the origin at the center of mass and let Oxyz be a principal axis frame of reference with the y axis directed along the moving axle AB. Let the Z axis lie along the fixed axle. Useful unit vectors are i, j, and k along the x, y, z axes and K along the Z axis.
sin cosθ θ= − +K i k
Angular velocity: φ θ= +K j! !ω
sin cosω φ θ θ φ θ= − + +i j k! ! !
Moments of inertia: 1 2, x y z yI e I I e I= =
Angular momentum about O:
0 x x y y z zI I Iω ω ω= + +H i j k
( )1 2sin cosyI e eφ θ θ φ θ= − + +i j k! ! !
The moment about the fixed Z axis is zero, hence constant.O ⋅ =H K
( )2 21 2 1sin cosO y yI e e I Cθ θ φ⋅ = + =H K !
( )2 211 1 0 2 0 02 2
1 2 sin cos
sin cosC C e e
e eφ θ θ φ
θ θ= = +
+! !
Twice the kinetic energy: 2 2 22 constantx x y y z zT I I Iω ω ω= + + =
( )2 2 2 21 22 sin cosyT I e eθ θ φ θ = + + +
! !
( )2 21 2y yI C I Cφ θ= + =! !
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2 2
2 1 2 0 1 0 C C C Cθ φ θ φ= − = +! ! ! !
Data: 2 2 21 2 1 21, 2 sin cos 1 cosθ θ θ= = + = +e e e e
0 0 090 , 0, 8 rad/sθ θ φ= ° = =! !
( )( )21 2
81 cos 90 8 8 rad/s 1 cos
C φθ
= + ° = =+
!
(a) min 28 4
1 cosφ
θ= =
+
min 4.00 rad/sφ =! !
( )( ) 22 0 8 8 64 rad/s= + =C
22 1C Cθ φ= −! !
(b) ( ) ( )( ) ( )2 2max 2 1 min 64 8 4 32 rad/sC Cθ φ= − = − =! !
max 5.66 rad/sθ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 132.
Let the Z axis be vertical. For principal axes xyz with origin at A, the principal moments of inertia are
( )22 21 1724 4x yI I I m a a ma ′ = = = + =
212zI I ma= =
Angular velocity components:
sin , , cosx y zω φ θ ω θ ω ψ φ θ= = − = +! ! !!
Angular momentum about A:
A x x y y z zI I Iω ω ω= + +H i j k
sin zI I Iφ θ θ ω′ ′= − +i j k! !
Kinetic energy: 2 2 21 1 12 2 2x x y y z zT I I Iω ω ω= + +
( )2 2 2 21 1sin2 2 zT I Iφ θ θ ω′= + +! !
Potential energy: 2 cosV mga θ= − Conservation of angular momentum about fixed Z axis:
( )sin cosA A θ θ⋅ = ⋅ +H K H i k
2sin coszI Iφ θ ω θ′= +!
2 2 217 1sin cos4 2 zma maφ θ ω θ α= + =! (1)
where α is a constant.
continued
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Conservation of energy: ,T V E+ = where E is a constant.
( )2 2 2 2 2 217 1sin 2 cos8 4 zma ma mga Eφ θ θ ω θ+ + − =! ! (2)
Constraint of clevis: 0 coszψ ω φ θ= = !!
(a) From (1), 2 2 2 2 2 2 2 20 0
17 1 17 1sin cos sin 90 cos 904 2 4 2m m m mma ma ma maφ θ φ θ φ φ+ = ° + °! ! ! !
2 2 017 1 17 17 1 17sin cos4 2 4 4 2 8m m
m
φθ θφ
+ = = =
!!
( )2 217 1 17sin 1 sin4 2 8m mθ θ+ − =
2 13sin , sin 0.65828 41.16930m m mθ θ θ= = = °
41.2mθ = °!
(b) At the minimum value of ,θ 0θ =!
From (2), ( )2 2 2 2 2 217 1sin 0 cos 2 cos8 4m m m m mma ma mgaφ θ φ θ θ+ + −! !
( )2 2 2 2 2 20 0 0
17 1sin 0 cos 90 2 cos908 4
ma ma mgaφ θ φ= + + ° − °! !
( ) ( )2 22 2 2 20
17 1 172 sin 2 cos 2 cos8 4 8m m mma mgaθ θ φ θ + − =
!
2 202.1250 1.5055ma mgaφ =!
20
32.20.70849 0.70849 30.4180.75
ga
φ = = =! 0 5.52 rad/sφ =! !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 133. Let the Z axis be vertical.
For principal axes xyz with origin at A, the principal moments of inertia are
( )22 21 1724 4x yI I I m a a ma ′ = = = + =
212zI I ma= =
Angular velocity components:
sin , , cosx y zω φ θ ω θ ω ψ φ θ= = − = +! ! !!
Angular momentum about A:
A x x y y z zI I Iω ω ω= + +H i j k
sin zI I Iφ θ θ ω′ ′= − +i j k! !
Kinetic energy: 2 2 21 1 12 2 2x x y y z zT I I Iω ω ω= + +
( )2 2 2 21 1sin2 2 zT I Iφ θ θ ω′= + +! !
Potential energy: 2 cosV mga θ= −
Conservation of angular momentum about fixed Z axis:
( )sin cosA A θ θ⋅ = ⋅ +H K H i k
2sin coszI Iφ θ ω θ′= +!
2 2 217 1sin cos4 2 zma maφ θ ω θ α= + =! (1)
where α is a constant.
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Conservation of energy: ,T V E+ = where E is a constant.
( )2 2 2 2 2 217 1sin 2 cos8 4 zma ma mga Eφ θ θ ω θ+ + − =! ! (2)
Constraint of clevis: 0 coszψ ω φ θ= = !!
(a) At 30 and at 90 , 0.m oθ θ θ θ θ= = ° = = ° =!
From (1), 2 2 2 2 2 20 0
17 1 17sin cos sin 04 2 4m m m mma ma maφ θ φ θ φ θ+ = +! ! !
22
2 20 0
17 1 1 3 17 68 4 2 2 2 4 23m mma maφ φ φ φ
+ = =
! ! ! !
From (2), 2 2
2 2 2 20 0
17 68 1 68sin 30 cos 30 2 cos308 23 4 23
ma ma mgaφ φ ° + ° − ° ! !
2 2 2 2 2 20 0
17 1sin 90 cos 90 2 cos908 4
ma ma mgaφ φ= ° + ° − °! !
22 2
017 3 68 17 2 cos3032 16 23 8
ma mgaφ + − = °
!
20
32.20.41660 0.41660 17.8860.75
ga
φ = = =!
0 4.2292 rad/sφ =! 0 4.23 rad/sφ =! !
(b) ( )68 4.229223mφ =! 12.50 rad/smϕ =! !
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Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 134. Let the Z axis be vertical with positive direction up.
For principal axes with the origin at A, the principal moments of inertia are
225zI ma=
( )22 22 2225 5x yI I ma m a ma= = + =
Unit vector along the Z axis: cos sinβ β= +k i k
Angular velocity: ω φ β= +k j!!
cos sinφ β β φ β= + +i j k!! ! Angular momentum about fixed point A:
A x x y y z zI I Iω ω ω= + +H i j k
2 2 222 22 2cos sin5 5 5
ma ma maφ β β βφ= + +i j k!! !
Kinetic energy:
2 2 21 1 12 2 2x x y y z zT I I Iω ω ω= + +
( )2 2 2 2 2 21 111cos sin5 5
ma maβ β φ β= + + !!
Potential energy: ( )2 sinV mg a β= −
Conservation of angular momentum about the fixed Z axis: ( ) ( )0A A⋅ = ⋅H K H K
2 2 2 20
22 2 22cos sin5 5 5
ma maφ β β φ + = ! !
02 211
11cos sinφφ
β β=
+
!!
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When max 1 02230 ,17
β β φ φ φ= = ° = =! ! ! (1)
Conservation of energy: 1 1 0 0T V T V+ = +
State 0: 0, 0, 0φ φ β β= = =!! !
State 1: 1, 30 , 0φ φ β β= = ° =!! !
( )2 2 2 2 2 21 0
1 1111cos 30 sin 30 2 sin 30 05 5
ma mga maφ φ° + ° − ° = +! !
2
2 2 20 0
17 22 1110 17 5
ma mga maφ φ − = ! !
2 20
1117
ma mgaφ =!
(a) 01711
ga
φ =! !
(b) From (1), 122 1717 11
ga
φ =! 14417
ga
φ =! !
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Chapter 18, Solution 135.
Let the Z axis be vertical.
For principal axes xyz with origin at A, the principal moments of inertia are
( )22 21 1724 4x yI I I m a a ma ′ = = = + =
212zI I ma= =
Angular velocity components:
sin , , cosx y zω φ θ ω θ ω ψ φ θ= = − = +! ! !!
Angular momentum about A:
A x x y y z zI I Iω ω ω= + +H i j k
sin zI I Iφ θ θ ω′ ′= − +i j k! !
Kinetic energy: 2 2 21 1 12 2 2x x y y z zT I I Iω ω ω= + +
( )2 2 2 21 1sin2 2 zT I Iφ θ θ ω′= + +! !
Potential energy: 2 cosV mga θ= −
Conservation of angular momentum about fixed Z axis:
( )sin cosA A θ θ⋅ = ⋅ +H K H i k
2sin coszI Iφ θ ω θ′= +!
2 2 217 1sin cos4 2 zma maφ θ ω θ α= + =! (1)
where α is a constant.
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Conservation of energy: ,T V E+ = where E is a constant.
( )2 2 2 2 2 217 1sin 2 cos8 4 zma ma mga Eφ θ θ ω θ+ + − =! ! (2)
Let the reference frame Axyz be turning with angular velocity
sin cosφ θ θ φ θΩ = − +i j k! ! !
Then ( )A A A AAxyzΣ = = + ×M H H H! ! Ω
( )sin sin zA
d dmga I I Idt dt
ωθ φ θ θ′ ′= − + + ×j i j k Η! !! Ω
z-component: 0 zΑ
dIdtω= + ⋅ ×k ΗΩ
0 0 10 sin cos 0
sin
z z z
z
d d dI I Idt dt dt
I I
ω ω ωφ θ θ φ θφ θ θ ω
= + − = + =′ ′−
! ! !! !
Integrating, zIω β= (3)
where β is a constant.
Data: 0 0 090 , 0, 0,θ φ θ= ° = =! !
From (3), 0zω ψ= !
From (1), 2 2 2 2 2 20
17 1 17 1sin cos sin 90 cos904 2 4 2z zma ma ma maφ θ ω θ φ ω+ = ° + °! !
22 cos
17 sinzω θφ
θ= −! (4)
From (2), ( )2 2 2 2 217 1sin 2 cos8 4 zma m mgaφ θ θ ω θ+ + −! !
( )2 2 2 2 20 0 0
17 1sin 2 cos908 4 zma m gmaφ θ θ ω= + + − °! !
or ( )2 2 2 217 sin 2 cos8
ma mgaφ θ θ θ+ =! !
(a) At ,mθ θ= 0θ =!
2 2 217 sin 2 cos8 m m mma mgaφ θ θ=!
22 2
217 2 cos sin 2 cos8 17 sin
z mm m
mma mgaω θ θ θ
θ
− =
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2 2 2
21 cos 2 cos34 sin
z mm
m
ma mgaω θ θθ
=
( )( )( )( )
22 2 2 2 0.75 50sin 0.85632cos 68 68 68 32.2
m z z
m
ma amga g
θ ω ωθ
= = = =
21 cos 0.85632cosm mθ θ− =
2cos 0.85632cos 1 0m mθ θ+ − =
[ ]1cos 0.85632 2.17561 0.65965, 1.5142mθ = − ± = −
( )1cos 0.65965 48.727mθ −= = ° 48.7mθ = °!
(b) From (4), 22 50cos 48.727 6.8694
17 sin 48.727mφ °= − = −! 6.87 rad/smφ = −! !
( )( )cos 50 6.8694 0.65965m z m mψ ω φ θ= − = − −!!
54.5 rad/smψ =! !
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Chapter 18, Solution 136.
Let the Z axis be vertical.
For principal axes xyz with origin at A, the principal moments of inertia are
( )22 21 172
4 4x yI I I m a a ma ′ = = = + =
21
2zI I ma= =
Angular velocity components:
sin , , cosx y zω φ θ ω θ ω ψ φ θ= = − = +& & &&
Angular momentum about A:
A x x y y z zI I Iω ω ω= + +H i j k
sin zI I Iφ θ θ ω′ ′= − +i j k& &
Kinetic energy: 2 2 21 1 1
2 2 2x x y y z zT I I Iω ω ω= + +
( )2 2 2 21 1sin
2 2 zT I Iφ θ θ ω′= + +& &
Potential energy: 2 cosV mga θ= −
Conservation of angular momentum about fixed Z axis:
( )sin cosA A θ θ⋅ = ⋅ +H K H i k
2sin coszI Iφ θ ω θ′= +&
2 2 217 1sin cos
4 2 zma maφ θ ω θ α= + =& (1)
where α is a constant.
Conservation of energy: ,T V E+ = where E is a constant.
( )2 2 2 2 2 217 1sin 2 cos
8 2 zma ma mga Eφ θ θ ω θ+ + − =& & (2)
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Let the reference frame Axyz be turning with angular velocity
sin cosφ θ θ φ θΩ = − +i j k& & &
Then ( )A A A AAxyzΣ = = + ×M H H H& & ΩΩΩΩ
( )sin sin zA
d dmga I I I
dt dt
ωθ φ θ θ′ ′= − + + ×j i j k Η& && ΩΩΩΩ
z-component: 0 zΑ
dI
dt
ω= + ⋅ ×k ΗΩΩΩΩ
0 0 1
0 sin cos 0
sin
z z z
z
d d dI I I
dt dt dtI I
ω ω ωφ θ θ φ θφ θ θ ω
= + − = + =′ ′−
& & &
& &
Integrating, zIω β= (3)
where β is a constant.
Data: 0 0 090 , 0, 0,θ φ θ= ° = =& &
From (3), 0zω ψ= &
From (1), 2 2 2 2 2 20
17 1 17 1sin cos sin 90 cos90
4 2 4 2z zma ma ma maφ θ ω θ φ ω+ = ° + °& &
2
2 cos
17 sinzω θφ
θ= −& (4)
From (2), ( )2 2 2 2 217 1sin 2 cos
8 4 zma m mgaφ θ θ ω θ+ + −& &
( )2 2 2 2 20 0 0
17 1sin 2 cos90
8 4 zma m mgaφ θ θ ω= + + − °& &
or ( )2 2 2 217sin 2 cos
8ma mgaφ θ θ θ+ =& &
(a) At ,mθ θ= 0θ =&
2 2 217sin 2 cos
8 m m mma mgaφ θ θ=&
2
2 22
17 2 cossin 2 cos
8 17 sinz m
m mm
ma mgaω θ θ θ
θ
− =
2 2 2
2
1 cos2 cos
34 sinz m
mm
mamga
ω θ θθ
=
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( )2 2
2 sin 32.2 sin 3068 68 842.78
cos 0.75 cos30m
zm
g
a
θωθ
° = = = °
29.031 rad/szω =
From (3), 0 zψ ω=& 0 29.0 rad/sψ =& !
(b) From (4), ( )
2
29.031 cos302
17 sin 30mφ
°= −
°& 11.83 rad/smφ = −& !
( )cos 29.031 11.83 cos30m z m mψ ω φ θ= − = − − °&& 39.3 rad/smψ =& !
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Chapter 18, Solution 137.
Use a rotating frame of reference with the y axis pointing into the paper.
Angular velocity of the frame:
sin cosφ θ θ φ θ+ +i j k& & &Ω = −Ω = −Ω = −Ω = −
Angular velocity of the top:
( )sin cosφ θ θ ψ φ θ= − + + +ω i j k& & &&
Its angular momentum about O.
O x x y y z zI I Iω ω ω= + +H i j k
( )sin cosI I Iφ θ θ ψ φ θ′ ′= − + + +i j k& & &&
where and .x y zI I I I I′= = =
The moment OM about O is due to the weight mg.
0 sinM mgc θ= j
(a) Since the fixed Z axis refers to a Newtonian frame of reference and
( ) 0,O ZM = it follows that ( )O Z
H is constant. Thus,
( ) ( )sin cosO O OZH θ θ= ⋅ = ⋅ − +H K H i k
( )2sin cos cosI Iφ θ ψ φ θ θ α′= + + =& && (1) !
where α is a constant.
continued
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( )O O O OOxyz= = + ×M H H H& & ΩΩΩΩ
( ) ( )sin sin cosd d
mgc I I Idt dt
θ φ θ θ ψ φ θ′ ′= − + + +j i j k& && &&
( )cos cosI Iψ φ θ θ φθ θ ′+ + − i& & & &&
( ) 2cos sin sin cosI Iψ φ θ φ θ φ θ θ ′+ + − j& & &&
z-components: ( )0 cosd
dtψ φ θ= + &&
Integrating, ( )cosI ψ φ θ β+ =&& (2) !
where β is a constant.
(b) Since cos ,zω ψ φ θ= + && constantz I
βω = = (3) !
From (1) and (2), 2sin cosI φ θ β θ α′ + =&
2
cos
sinI
α β θφθ
−=′
& (4) !
which is a function of .θ
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Chapter 18, Solution 138.
(a) Angular velocity of the top:
( )sin cosφ θ θ ψ φ θ= − + + +ω i j k& & &&
Kinetic energy:
2 2 21 1 1
2 2 2x x y y z zT I I Iω ω ω= + +
( )2 2 21 1 1sin
2 2 2 zI I Iφ θ θ ω′ ′= + +& &
Potential energy: cosV mgc θ=
Principle of conservation of energy: T V E+ =
( )2 2 21 1 1sin cos
2 2 2 zI I I mgc Eφ θ θ ω θ′ ′+ + + =& & !
(b) Solving for 2,θ&
( ) ( )22 212 2 cos sinzE I mgc
Iθ ω θ φ θ= − − −
′& & (A)
Equation (2) of Problem 18.137, with coszω ψ φ θ= + && gives
2
2zI
I
βω = (B)
Equation (1) of Problem 18.137 gives
2sin cosI φ θ β θ α′ + =& (C)
2
cos
sinI
α β θφθ
−=′
& (D)
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Substituting Equations (D) and (B) into Equation (A),
( )2 ,fθ θ=&
where ( )221 cos
2 2 cossin
f E mgcI I I
β α β θθ θθ
− = − − − ′ ′ (1) !
(c) Maximum and minimum values of θ occur when ( ) 0.f θ = Setting cos xθ = and 2 2sin 1 xθ = − in
Equation (1), and letting ( ) 0f θ = gives
( )( ) ( )
22
2 2
12 2 0
1
xE mgcx
I I I x
α ββ −− + − = ′ ′ −
Multiplying by ( )21I x′ − gives the cubic equation ( ) 0:F x =
( ) ( )2
22 12 2 1 0E mgcx x x
I I
β α β
− − − − − = ′ (2) !
Solving this equation will yield three values of x. The two values lying between 1− and 1+ correspond to the maximum and minimum values of .θ
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Chapter 18, Solution 139.
Data: 360 mm 0.06 m, 180 mm 0.18 m, 0.135 m,4
r h c h= = = = = =
0 0 0 030 , 300 rad/s, 20 rad/s, 0θ ψ φ θ= ° = = =! !!
Calculate the following:
( )22 3 23 3 0.06 1.08 10 m10 10
I rm
−= = = ×
( ) ( )2 22 2 3 23 1 3 1 0.06 0.18 19.98 10 m5 4 5 4
I r hm
−′ = + = + = ×
Initially, 0 0 0sin 20sin 30 10 rad/s, 0x yω φ θ ω θ= − = − ° = − = =! !
0 0 0cos 300 20cos30 317.32 rad/szω ψ φ θ= + = + ° =!!
( )2 2 21 12 2x y z
T I Im m m
ω ω ω′= + +
( )( ) ( )( )23 2 3 2 21 119.98 10 10 0 1.08 10 317.32 55.3728 m /s2 2
− −= × + + × =
( )( ) 2 20cos 9.81 0.135 cos30 1.1469 m /sV gc
mθ= = ° =
( ) 2 22 2 55.3728 1.1469 113.0394 m /sEm
= + =
( )( )3 21.08 10 317.32 0.342706 m /szI
m mβ ω −= = × =
( )( )2 3 20 0 0sin cos 19.98 10 20 sin 30 0.342706cos30I
m mα φ θ β θ −′
= + = × ° + °!
20.396692 m /s=
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After dividing by m, Equation (2) of Problem 18.138 becomes
( ) ( )2
22
22 2 1 0mIm
E m xF x gcx xm I m m
βα β
= − − − − − = ′
( ) ( )( )( ) ( ) ( )2 22
3 30.342706 0.396692 0.342706
113.0394 2 9.81 0.135 1 01.08 10 19.98 10
xx x− −
− − − − − =
× ×
( )( ) ( )224.29198 2.6487 1 5.87825 1.157529 0x x x− − − − =
(a) Roots are: cos 0.68170, 0.86603, 2.2919x θ= =
( )1max cos 0.68170 47.023θ −= = ° max 47.0θ = °!
(b) By Equation (4) of Problem 18.137,
( )( )( )2 3 2
0.396692 0.342706 0.68170cos 15.2474sin 19.98 10 sin 47.023I
α β θφθ −
−−= = =′ × °
!
317.32 rad/szω =
( )( )cos 317.32 15.2474 0.68170zψ ω φ θ= − = −!! spin: 307 rad/sψ =! !
precession: 15.25 rad/sφ =! !
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Chapter 18, Solution 140.
Data: 360 mm 0.06 m, 180 mm 0.18 m, 0.135 m4
r h c h= = = = = =
0 0 0 030 , 300 rad/s, 4 rad/s, 0θ ψ φ θ= ° = = − =! !!
Calculate the following:
( )22 3 23 3 0.06 1.08 10 m10 10
I rm
−= = = ×
( ) ( )2 22 2 3 23 1 3 1 0.06 0.18 19.98 10 m5 4 5 4
I r hm
−′ = + = + = ×
Initially, ( )0 0 0sin 4 sin 30 2 rad/s, 0x yω φ θ ω θ= − = − − ° = = =! !
( )300 4 cos30 296.536 rad/szω = + − ° =
( )2 2 21 12 2x y z
T I Im m m
ω ω ω′= + +
( ) ( )( ) ( )( )2 23 3 2 21 119.98 10 2 0 1.08 10 296.536 47.5241 m /s2 2
− −= × + + × =
( )( ) 2 2cos 9.81 0.135 cos30 1.1469 m /sV gcm
θ= = ° =
( ) 2 22 2 47.5241 1.1469 97.3419 m /sEm
= + =
( )( )3 21.08 10 296.536 0.320259 m /szI
m mβ ω −= = × =
( )( )2 3 20 0 0sin cos 19.98 10 4 sin 30 0.320259cos30I
m mα φ θ β θ −′
= + = × − ° + °!
20.257372 m /s=
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After dividing by m, Equation (2) of Problem 18.138 becomes
( ) ( )2
22
22 2 1 0mIm
E m xF x gcx xm I m m
βα β
= − − − − − = ′
( ) ( )( )( ) ( ) ( )2 22
3 30.320259 0.257372 0.320259
97.3419 2 9.81 0.135 1 01.08 10 19.98 10
xx− −
− = − − − − =
× ×
( )( ) ( )222.37324 2.6487 1 5.13342 0.80364 0x x x− − − − =
(a) Roots are: cos 0.23732, 0.86603, 1.73x θ= =
( )1max cos 0.23732 76.272θ −= = ° max 76.3θ = °!
(b) By Equation (4) of Problem 18.137,
( )( )( )2 3 2
0.257372 0.320259 0.23732cos 9.6192 rad/ssin 19.98 10 sin 76.272I
α β θφθ −
−−= = =′ × °
!
296.536 rad/szω =
( )( )cos 296.536 9.6192 0.23732zψ ω φ θ= − = −!! spin: 294 rad/sψ =! !
precession: 9.62 rad/sφ =! !
(c) 2cos 0
sinIα β θφ
θ−= =′
!
0.257372cos0.320259
αθβ
= = 36.5θ = °!
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Chapter 18, Solution 141.
(a) From Equation (18.27), O OΣ =M H!
Since 0, 0.O OΣ = =M H! constant (1)O =H !
Conservation of energy: T V+ = constant
Since 0,V = constant (2)T = !
For a rigid body rotating about point O, ( )2 2 212 xx y y z zT I I Iω ω ω= + +
, O x x y y z z x y zH I I Iω ω ω ω ω ω= + + = + +i j k i j kω
2 2 2 2x y zO x y zI I I Tω ω ω ω⋅ = + + =H
Let β be the angle between the vectors OH and .ω
cosO OH ω β⋅ =H ω
The projection of ω along is cosO ω βH
2cos constantO
TH
ω β = = cos constant (3)ω β = !
(b) cosω β is the perpendicular distance from the invariable plane. This distance is equal to 2 .O
TH
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(c) For a frame of reference attached to the body, the moments of inertia with respect of orthogonal axes of the frame do not change.
2 2 2 2x x y y z zI I I Tω ω ω+ + = (4)
Let 1 1 12 2 2, ,
x y z
T T Ta b cI I I
= = = (5)
Then, 1 1 1
22 2
2 2 2 1yx z
a b cωω ω+ + = (6)
which is the equation of an ellipsoid.
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Chapter 18, Solution 142.
(a) From Problem 18.141, the equation of the Poinsot ellipsoid is
2 2 2 2 constantx y zx y zI I I Tω ω ω+ + = =
Let ( ) 2 2 2, ,x y zx y z x y zF I I Iω ω ω ω ω ω= + +
grad x y z
F F FF
ω ω ω∂ ∂ ∂= + +∂ ∂ ∂
i j k
2 2 2 2x x y y z z OI I Iω ω ω= + + =i j k H
The direction of the normal at a point on the surface of the ellipsoid is parallel to grad F, which, in turn is parallel to .OH Since OH is normal also to the invariable plane, it follows that the Poinsot ellipsoid is tangent to the invariable plane at the point common to the plane and the ellipsoid.
(b) The Poinsot elipsoid moves with the body. Thus, its angular velocity is ,ωωωω the angular velocity of the body. Since point O is regarded as fixed, the angular velocity vector lies along the axis of rotation, or the locus of points of zero velocity. Thus, the velocity of the point of contact of the Poinsot ellipsoid with the invariable plane is zero. The Poinsot ellipsoid rolls without slipping on the invariable plane.
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Chapter 18, Solution 143.
Let and x y zI I I I I′= = = so that the z axis is the symmetry axis. Then, the equation of the Poinsot ellipsoid
(Equation (4) of Problem 18.141) becomes
( )2 2 2 2 constantx y zI I Tω ω ω′ + + = =
which is the equation of an ellipsoid of revolution. It follows that the tip of ωωωω describes circles on both the Poinsot ellipsoid and on the invariable plane, and that the vector ωωωω itself describes circular body and space cones. The Poinsot ellipsoid, the invariable plane, and the body and space cones are shown below for cases a and b.
(a) I I ′< (b) I I ′>
Direct Precession Retrograde Precession
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Chapter 18, Solution 144.
(a) Equation (1) expresses conservation of energy as shown in the solution to Problem 18.141. It is the
equation of the Poinsot ellipsoid.
Let 1 1 12 2 2, ,
x y z
T T Ta b cI I I
= = =
Then, 22 2
2 2 21 1 1
1yx z
a b cωω ω+ + = (3)
which is the equation of an ellipsoid.
Equation (2) expresses the constancy of ( ) ( ) ( )2 2 22O O O Ox y zH H H H= + + , the square of the magnitude
of the angular momentum vector.
Let 2 2 2, , O O O
x y z
H H Ha b cI I I
= = =
Then, 22 2
2 2 22 2 2
1yx z
a b cωω ω+ + = (4)
which is the equation of a second ellipsoid. Since the coordinates , , x y zω ω ω of the tip of the vector ω must satisfy both Equations (1) and (2), the curve described by the tip of ω is the intersection of the two ellipsoids.
(b) Assume .x y zI I I> >
Then, 1 1 1 2 2 2 and .a b c a b c< < < <
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Thus, for both ellipsoids, the minor axis is directed along the x axis, the intermediate axis along the y axis, and the major axis along the z axis. However, because the ratio of the major to minor
semi axis is x
z
II
for the Poinsot ellipsoid and is x
z
II
for the second
ellipsoid, the deviation from a spherical shape is more pronounced in the second ellipsoid.
The largest ellipsoid of the second type to be in contact with the Poinsot ellipsoid will lie outside that ellipsoid and touch it at its points of intersection with the x axis, and the smallest will lie inside the Poinsot ellipsoid and touch it at its points of intersection with the z axis (see left-hand sketch). All ellipsoids of the second type comprised between these two will intersect the Poinsot ellipsoid along the curves called polhodes, as shown in the right-hand figure.
Note that the ellipsoid of the second type, which has the same intermediate axis as the Poinsot ellipsoid, intersects that ellipsoid along two ellipses whose planes contain the y axis. These curves are not polhodes, since the tip of ω will not describe them, but they separate the polhodes into four groups. Two groups loop around the minor axis (x axis) and the other two around the major axis (z axis).
(c) If the body is set to spin about one of the principal axes, the Poinsot ellipsoid will remain in contact with the invariable plane at the same point (on the x, y, or z axis); the rotation is steady. In any other case, the point of contact will be located on one of the polhodes, and the tip of ω will start describing that polhode, while the Poinsot ellipsoid rolls on the invariable plane.
A rotation about the minor or the major axis (x or z axis) is stable. If that motion is disturbed, the tip of ω will move to a very small polhode surrounding that axis and stay close to its original position.
On the other hand, a rotation about the intermediate axis (y axis) is unstable. If that motion is disturbed, the tip of ω will move to one of the polhodes located near that axis and start describing it, departing completely from its original position and causing the body to tumble.
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Chapter 18, Solution 145.
230.093168 lb s /ft, 24 in. 2 ft,
32.2
Wm l
g= = = ⋅ = =
( )12 rad/s=ω i
For rod ADB, 0, since 0.D x xI Iω= ≈ ≈H i
For rod CDE, use principal axes , x y′ ′ as shown.
9cos , 41.410
12θ θ= = °
2cos 9 rad/sxω ω θ′ = =
2sin 7.93725 rad/syω ω θ′ = =
0zω ′ =
0′ ≈xI
( )( )221 10.093168 2
12 12yI ml′ = =
20.0310559 lb s ft= ⋅ ⋅
D x x y y z zI I Iω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +H i j k
( )( )0 0.0310559 7.93725 0′= + +j
0.246498 ′= j
0.246 lb s ftDH = ⋅ ⋅ !
( )0.246498 sin cos 0.163045 0.184874D θ θ= + = +H i j i j
0.163045
cos0.246498xθ = 48.6θ = °x !
0.184874
cos0.246498
θ =y 41.4θ = °y !
cos 0zθ = 90θ = °z !
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Chapter 18, Solution 146.
230.093168 lb s /ft, 24 in. 2 ft,
32.2
Wm l
g= = = ⋅ = =
( )12 rad/s=ω i
For rod ADB, 0, since 0.D x xI Iω= ≈ ≈H i
For rod CDE, use principal axes , x y′ ′ as shown.
9cos , 41.410
12θ θ= = °
2cos 9 rad/sxω ω θ′ = = 2sin 7.93725 rad/syω ω θ′ = =
0zω ′ =
0xI ′ ≈
( )( )221 10.093168 2
12 12yI ml′ = =
20.0310559 lb s ft= ⋅ ⋅
2 2 2 21 1 1 1
2 2 2 2x y zx y zT mv I I Iω ω ω′ ′ ′′ ′ ′= + + +
( )( )10 0 0.0310559 7.93725 0
22= + + +
0.97826 ft lb= ⋅ 0.978 ft lbT = ⋅ !
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Chapter 18, Solution 147.
Let 1
6m m′ = be the mass of one side of the cube. Choose x, y, and z axes perpendicular to the faces of the
cube. Let a be the side of the cube.
For a side perpendicular to the x axis, ( ) 21
1.
6xI m a′=
For a side perpendicular to the y or z axis, ( ) 2 22
1 1 1
12 4 3xI m a m a ′ ′= + =
Total moment of inertia: ( ) ( ) 2 21 2
5 52 4
3 18x x xI I I m a ma′= + = =
By symmetry, y xI I= and .z xI I=
Since all three moments of inertia are equal the ellipsoid of inertia is a sphere. All centroidal axes are principal axes.
Moment of inertia about the vertical axis: 25
18vI ma=
Let 2
3b a= be the moment arm of the impulse applied to the corner.
Using the impulse-momentum principle and taking moments about the vertical axis,
( ) 25
18v vbF t H I maω ω∆ = = = (1)
Data: ( )21.5 m, 1.5 1.22474 m
3a b= = =
21.25664 rad/s, 50 N, 1.2 s.
5F t
πω = = = ∆ =
Solving Equation (1) for m, ( ) ( )( )( )
( ) ( )2 2
1.22474 50 1.218 1893.563 kg
5 5 1.5 1.25664
bF tm
a ω∆
= = = 93.6 kgm = !
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Chapter 18, Solution 148.
( )2 2 2 22G x x y y z z x x y y zI I I m k k kω ω ω ω ω ω= + + = + +H i j k i j k
( ) ( ) ( ) ( ) ( ) ( )2 2 250002.45 0.040 2.65 0 2.55 0.060
32.2 = + +
i j k
( ) ( )37.283 lb s ft 60.582 lb s ft= ⋅ ⋅ + ⋅ ⋅i k
Let , , ,A B C− − −j j j and D− j be the impulses provided by the 5-lb thrusters at A, B, C, and D respectively. Let Ej be that provided by the 125-lb main thruster.
Position vectors for intersections of the lines of action of the truster impulses with the xz plane.
( )14 2 ft, 2 2 2 4.8284 ft
2a b= = = + =
, A Ba b a b= − + = +r i k r i k
, C Da b a b= − = − −r i k r i k
The final linear and angular momenta are zero.
Principle of impulse-momentum. Moments about G:
( ) ( ) ( ) ( ) 0G A B C DA B C D+ × − + × − + × − + × − =H r j r j r j r j
( ) ( ) 0G b A B C D a A B C D+ + − − + − − + =H i k
Resolve into components.
( ) 37.283
: 7.7216 lb s4.8284
G xH
A B C Db
+ − − = − = − = − ⋅i (1)
( ) 60.582
: 30.291 lb s2
G zH
A B C Da
− − + = − = − = − ⋅k (2)
Of A, B, C, and D, two must be zero or positive, the other two zero.
Set 0A = and .B D N− = Solve the simultaneous equations (1) and (2).
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19.006 lb sC = ⋅ and 11.285 lb s.N = ⋅ Set 0D = and 11.285 lb sB = ⋅
(a) Use thrusters C and B. !
(b) ( ) 19.006,
5C C CC
CF t C t
F∆ = ∆ = = 3.80 sCt∆ = !
( ) 11.285,
5B B BB
BF t B t
F∆ = ∆ = = 2.26 sBt∆ = !
(c) Linear momentum: 0, 30.291 lb sE B C E− − = = ⋅j j j
( ) 30.291
125E E EE
EF t E t
F∆ = ∆ = = 0.242 sEt∆ = !
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Chapter 18, Solution 149.
For the ′x and ′y axes shown, the initial angular velocity 0ω j has components
0 02 2
, ,2 2
ω ω ω ω′ ′= =x y
Initial angular momentum about the mass center:
( ) ( )200
1 2
12 2ω ω ω′ ′ ′ ′′ ′ ′ ′= + = +G x x y yI I maH i j i j
Initial velocity of the mass center: 0 0=v
Let ωωωω be the angular velocity and v be the velocity of the mass center immediately after impact. Let
( )F t∆ k be the impulse at B.
Kinematics: ( ) ( )/ ω ω ω′ ′ ′′ ′ ′ ′= × = + + × −B B A x y z av r i j k jωωωω
( )B z xa ω ω′ ′ ′= −v i k
Since the corner B does not rebound, ( ) 0 or 0ω ′′ = =B xzv
( ) ( ) ( )/1 1
2 2G A y z z z ya aω ω ω ω ω′ ′ ′ ′ ′ ′ ′ ′ ′ ′= × = + × − − = − +
v r j k i j i j kωωωω
Also, ( )2/
12
4ω ω ω′ ′ ′′ ′ ′× = − + +G A y y zm mar v i j k
and
2 21 1
12 6ω ω ω ω ω′ ′ ′ ′ ′ ′ ′ ′′ ′ ′ ′ ′= + + = +G x x y y z z y zI I I ma maH i j k j k
Principle of impulse-momentum:
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Moments about A: ( ) ( ) ( )0A Aa F t+ − × ∆ =H j k H
( ) ( )/ 0 /0G G A G G Am aF t m+ × − ∆ = + ×H r v i H r v
Resolve into components.
( )2 20
1 1: 2
24 4 yma aF t maω ω ′′ − ∆ = −i
2 2 20 0
1 1 1 2: 2
24 12 4 8y y yma ma maω ω ω ω ω′ ′ ′′ = + =j
2 21 1: 0 0
6 2z z zma maω ω ω′ ′ ′′ = + =k
(a) ( )0 02 1 2
28 8 2
ω ω′= = −j j iωωωω ( )01
8ω= − +i jωωωω !
(b) 01 2
2 16ω ω′= =ya av k k 00.0884 ω= av k!
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Chapter 18, Solution 150.
For the simpler x′ and y′ axes, the initial angular velocity 0ω j has components
0 02 2
, ,2 2
ω ω ω ω′ ′= =x y
Initial angular momentum about the mass center:
( ) ( )200
1 2
12 2ω ω ω′ ′ ′ ′′ ′ ′ ′= + = +G x x y yI I maH i j i j
Initial velocity of the mass center: 0 0=v
Let ωωωω be the angular velocity and v be the velocity of the mass center immediately after impact. Let
( )F t∆ k be the impulse at B.
Kinematics: ( ) ( )/ ω ω ω′ ′ ′′ ′ ′ ′= × = + + × −B B A x y z av r i j k jωωωω
( )B z xa ω ω′ ′ ′= −v i k
Since the corner B does not rebound, ( ) 0 or 0ω ′′ = =B xzv
( ) ( ) ( )/1 1
2 2G A y z z z ya aω ω ω ω ω′ ′ ′ ′ ′ ′ ′ ′ ′ ′= × = + × − − = − +
v r j k i j i j kωωωω
Also, ( )2/
12
4ω ω ω′ ′ ′′ ′ ′× = − + +G A y y zm mar v i j k
and
2 21 1
12 6ω ω ω ω ω′ ′ ′ ′ ′ ′ ′ ′′ ′ ′ ′ ′= + + = +G x x y y z z y zI I I ma maH i j k j k
Principle of impulse-momentum:
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Moments about A: ( ) ( ) ( )0A Aa F t′+ − × ∆ =H j k H
( ) / 0 /0G G A G G Am aF t m′+ × + ∆ = + ×H r v i H r v
Resolve into components.
( )2 20
1 1: 2
24 4 yma aF t maω ω ′′ − ∆ = −i (1)
2 2 20 0
1 1 1 1: 2 2
24 12 4 8y y yma ma maω ω ω ω ω′ ′ ′′ = + =j
2 21 1: 0 0
6 2z z zma maω ω ω′ ′ ′′ = + =k
(a) From (1), 0 0 01 1 7
2 2 224 32 96
F t ma ma maω ω ω∆ = + =
( ) 00.1031F t maω∆ =k k!
01 1
22 16
ω ω′ ′= =ya av k k
Linear momentum: 0m t F t m+ ∆ + ∆ =v A k v
0 07 1
0 2 296 16
ω ω′ ′+ ∆ + =t ma maA k k
(b) 01
296
ω∆ = −t maA 00.01473 ω∆ = −t maA k!
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Chapter 18, Solution 151.
( )23 0.093168 lb s /ft, 24 in. 2 ft, 12 rad/s32.2
= = = ⋅ = = =wm lg
iω
For rod ADB, 0, since 0.D x xI Iω= ≈ ≈H i
For rod CDE, use principal axes , ′ ′x y as shown.
9cos , 41.41012
θ θ= = °
2cos 9 rad/sω ω θ′ = =x
2sin 7.93725 rad/sω ω θ′ = =y
0ω ′ =z
( )296 rad/sα = − i
cos 72 rad/sα α θ′ = = −x
2sin 63.498 rad/sα α θ′ = = −y
0′ ≈xI
( )( )22 21 1 0.093168 2 0.0310559 lb s ft12 12yI ml′ = = = ⋅ ⋅
′ ′=z yI I
ω ω ω′ ′ ′ ′ ′ ′′ ′ ′= + +D x x y y z zI I IH i j k
( )( ) ( )0 0.0310559 7.93725 0 0.246498 lb s ft ′= + + = ⋅ ⋅j j
Let the reference frame D x′y′z′ be rotating with angular velocity
( ) ( )9 rad/s 7.93725 rad/sx yω ω ω′ ′′ ′ ′ ′= = + = +i i j i jΩ
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( ) ′ ′ ′= + ×! !
D D DDx y zH H HΩ
α α α′ ′ ′ ′ ′ ′′ ′ ′= + + + ×x x y y z z DI I Ii j k HΩ
( )( ) ( ) ( )0 0.0310559 63.498 0 9 7.93725 0.246498′ ′ ′= + − + + + ×j i j j
1.97199 2.21848′= − +j k
( )( ) ( )1.97199 lb ft sin cos 2.21848 lb ftθ θ= − ⋅ + + ⋅i j k
( ) ( ) ( )1.304 lb ft 1.479 lb ft 2.22 lb ftD = − ⋅ − ⋅ + ⋅H i j k! !
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Chapter 18, Solution 152.
( ) ( )2 2 75040 1.24224 lb s /ft, 78.54 rad/s32.2 60
π= = ⋅ = =m i iω
(a) The force-couple system acting on the wheel is ( ) ( )36.2 lb , 10.85 lb ft′ ′= − = − ⋅CF j M k
22 nm m y z
mω
ω′′ = = − = + = FF a r r j k
( )( )3
2 236.2 4.7241 10 ft 0.0567 in.
1.24224 78.54ω−′
= = = × =yFy y
m
2 0ω
′= =zFz
m 0.0567 in.=r !
ω ω ω= − −C x xy xzI I IH i j k
( )ω ω ω ω′ = = × = × − −!C C C x xy xzI I IM H H i i j kω
( ) ( ) 2 2ω ω′ ′+ = −C C xz xyy zM M I Ij k j k
( ) ( )( )
3 22 2
10.851.75893 10 lb s /ft
78.54ω−′ − −
= − = = × ⋅C zxy
MI
3 21.759 10 lb s ft−= × ⋅ ⋅xyI !
( )
2 0ω
′= =
C yxz
MI 0=xzI !
(b) Positions for the balance masses. 7.25 in. 0.60417 ft= = − = − = =A B E Dy y y y
3 in. 0.25 ft− = = = − = =A B E Dx x x x
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Balance masses must be added to move the mass center to point C and to reduce the product of inertia to zero.
0+ + + + =A A B B E E D Dm y m y m y m y my
( )( ) ( )( )30.60417 1.24224 4.7241 10−+ − − + ×A B E Dm m m m
39.7133 10−+ − − = − ×A B E Dm m m m (1)
0+ + + + =A A A B B B E E E D D D xym x y m x y m x y m x y I
( )( )( ) 30.25 0.60417 1.75893 10 0−− + − + + × =A B E Dm m m m
11.6452− + − + = −A B E Dm m m m (2)
To solve (1) and (2), set 0=Bm and let = −AD A Dm m m .
Then, 39.7133 10−− = − ×AD Em m
and 311.6452 10−− − = − ×AD Em m
Solving, 3 2 3 20.9660 10 lb s /ft, 10.6792 10 lb s /ftAD Em m− −= × ⋅ = × ⋅
Set 0,=Dm so that 3 20.9660 10 lb s /ft.Am −= × ⋅
Then, ( )( )310.6792 10 32.2 0.3439 lb,−= = × =E EW m g 5.50 oz=EW !
( )( )30.9660 10 32.2 0.0311 lb,A AW m g −= = × = 0.498 ozAW = !
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Chapter 18, Solution 153.
( )( )1
2 2500261.8 rad/s
60
π= =ωωωω 1 1ω= kωωωω
Angular velocity: 2 1ω ω= +j kωωωω
Angular momentum of rotor: 2 1G y zI Iω ω= +H j k
Let the reference frame Gxyz be rotating with angular velocity 2 .ω= jΩΩΩΩ
( ) ( )2 2 1 1 20G G G y z zGxyzI I Iω ω ω ω ω= + × = + × + =H H H j j k i& & ΩΩΩΩ
Couple exerted on the saw: 21 2 1 2G z zI mkω ω ω ω= = =M H i i&
( )( ) ( )( )231.75 30 10 261.8 2.4−= × −M i ( )0.990 N m= − ⋅M i!
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Chapter 18, Solution 154.
Angular velocity of shaft DE and arm CBA: 2ω= iΩ
Angular velocity of disk A: 2 1ω ω= +i jω
Angular momentum about its mass center A:
2 22 1 2 1
1 14 2A x x y y z z x yI I I I I mr mrω ω ω ω ω ω ω= + + = + = +H i j k i j i j
Let the reference frame Oxyz be rotating with angular velocity 2 .ω= iΩ
( ) 2 22 1 2
1 14 2A A A AOxyz
mr mrω ω ω= + × = + + ×H H H i j i H! ! ! !Ω
2 2 22 1 1 2
1 1 14 2 2
mr mr mrω ω ω ω= + +i j k! !
Velocity of point A: ( )2 / 2 2 2A A O b c b cω ω ω ω= × = × − + = +v i r i k j j k
Acceleration of point A: 2 / 2A A O Aω ω= × + ×a j r j v!
( ) ( )2 22 2 2 2A b c c bω ω ω ω= − + +a j k! !
Consider the system of particles consisting of the shaft, the arm, and the disk. Neglect the mass of the arm.
AmΣ =F a
y z y z AD D E E m+ + + =j k j k a
Resolve into components.
( )22 2y yD E m b cω ω+ = −!
( )22 2z zD E m c bω ω+ = +!
/D D A A D AmΣ = = + ×M H H r a! !
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( ) ( ) ( )0 2 y z A AM l E E l c b m+ × + = + + − ×i i j k H i j k a!
( ) 2 2 2 2 20 2 1 2 2
1 12 24 2z yM lE lE m r b c m r lc lbω ω ω ω − + = + + + − −
i j k i j! ! !
2 21 2 2 2
12
m r lb lcω ω ω ω + + −
k!
2 2 20 2
1: 4
M m r b c ω = + +
i !
2 2 2 21 2 2 2 1 2 2 2
1 1: , 2 2 2 2y ym mE r lb lc D r lb lcl l
ω ω ω ω ω ω ω ω = + − = − + −
k ! !
2 2 2 22 2 1 2 2 1
1 1: , 2 2 2 2z zm mE lc lb r D lc lb rl l
ω ω ω ω ω ω = + − = + +
j ! ! ! !
Data: 3 kg, 0.2 m, 0.225 m, 0.3 m= = = = =m r b c l
1 1 2 216 rad/s, 0, 8 rad/s, 0ω ω ω ω= = = =! !
( )( ) ( ) ( )( ) ( )( )( )2 23 1 0.2 16 8 0 0.3 0.225 8 34.4 N2 0.3 2yD = − + − = −
( )( ) ( )( )( )23 0 0.3 0.225 8 0 21.6 N2 0.3zD = + + =
( ) ( )34.4 N 21.6 N= − +D j k!
( )( ) ( ) ( )( ) ( )( )( )2 23 1 0.2 16 8 0 0.3 0.225 8 8.80 N2 0.3 2yE = + − = −
( )( ) ( )( )( )23 0 0.3 0.225 8 0 21.6 N2 0.3zE = + + =
( ) ( )8.80 N 21.6 N= − +E j k!
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Chapter 18, Solution 155.
Angular velocity of shaft DE and arm CBA: 2ω= iΩ
Angular velocity of disk A: 2 1ω ω= +i jω
Angular velocity about its mass center A:
2 22 1 2 1
1 14 2A x x y y z z x yI I I I I mr mrω ω ω ω ω ω ω= + + = + = +H i j k i j i j
Let the reference frame Oxyz be rotating with angular velocity 2 .ω= iΩ
( ) 2 22 1 2
1 14 2A A A AOxyz
mr mrω ω ω= + × = + + ×H H H i j i H! ! ! !Ω
2 2 22 1 1 2
1 1 14 2 2
mr mr mrω ω ω ω= + +i j k! !
Velocity of point A: ( )2 / 2 2 2A A O b c b cω ω ω ω= × = × − + = +v i r i k j j k
Acceleration of point A: 2 / 2A A O Aω ω= × + ×a j r j v!
( ) ( )22 2 2 2A b c c bω ω ω ω= − + +a j k! !
Consider the system of particles consisting of the shaft, the arm, and the disk. Neglect the mass of the arm.
AmΣ =F a
y z y z AD D E E m+ + + =j k j k a
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Resolve into components.
( )22 2y yD E m b cω ω+ = −!
( )22 2z zD E m c bω ω+ = +!
/D D A A D AmΣ = = + ×M H H r a! !
( ) ( ) ( )2O y z A AM l E E l c b m+ × + = + + − ×i i j k H i j k a!
( ) 2 2 2 2 22 1 2 2
1 12 24 2O z yM lE lE m r b c m r lc lbω ω ω ω − + = + + + − −
i j k i j! ! !
2 21 2 2 2
12
m r lb lcω ω ω ω + + −
k!
2 2 22
1: 4OM m r b c ω = + +
i !
2 2 2 21 2 2 2 1 2 2 2
1 1: , 2 2 2 2y ym mE r lb lc D r lb lcl l
ω ω ω ω ω ω ω ω = + − = − + −
k ! !
2 2 2 22 2 1 2 2 1
1 1: , 2 2 2 2z zm mE lc lb r D lc lb rl l
ω ω ω ω ω ω = + − = + +
j ! ! ! !
Data: 3 kg, 0.2 m, 0.225 m, 0.3 mm r b c l= = = = = 2
1 1 2 216 rad/s, 0, 8 rad/s, 6 rad/sω ω ω ω= = = =! !
(a) ( ) ( ) ( ) ( ) ( )2 2 213 0.2 0.225 0.225 64OM = + +
( )2.00 N mO = ⋅M i!
(b) ( )( ) ( ) ( )( ) ( )( )( ) ( )( )( )2 23 1 0.2 16 8 0.3 0.225 6 0.3 0.225 8 32.4 N2 0.3 2yD = − + − = −
( )( ) ( )( )( ) ( )( )( )23 0.3 0.225 6 0.3 0.225 8 0 23.6 N2 0.3zD = + + =
( ) ( )32.4 N 23.6 N= − +D j k!
( )( ) ( ) ( )( ) ( )( )( ) ( )( )( )2 23 1 0.2 16 8 0.3 0.225 6 0.3 0.225 8 6.78 N2 0.3 2yE = + − = −
( )( ) ( )( )( ) ( )( )( )23 0.3 0.225 6 0.3 0.225 8 0 23.6 N2 0.3zE = + + =
( ) ( )6.78 N 23.6 N= − +E j k !
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
Chapter 18, Solution 156.
( )02 rad 1 h36 rev/h 0.062832 rad/s
rev 3600 sπω = =
25000 155.28 lb s /ft32.2
= = ⋅m
( )( )22 2155.28 2.7 1131.99 lb s ft= = = ⋅ ⋅x xI mk
21131.99 lb s ft= = ⋅ ⋅z xI I
( )( )22 2155.28 2.94 1342.17 lb s ft= = = ⋅ ⋅y yI mk
( ) ( )( ) ( )00 1342.18 0.062832 84.331 lb s ftω= = = ⋅ ⋅H j j jG yI
1.8 ft, 1.8 3.6cos 45 4.3456 ft= = + ° =a b
When thrusters A and B are activated,
( ) ( )( ) ( )4.3456 10 43.456 lb ftG A Bb F F= − + = − = − ⋅M i i i
Angular momentum after 2 s:
( ) ( ) ( )( )0 84.331 43.456 2G G G t= + ∆ = + −H H M j i
( ) ( )86.912 lb s ft 84.331 lb s ft= − ⋅ ⋅ + ⋅ ⋅i j
86.912 0.076778 rad/s 43.991 rev/h1131.99
ω = = − = − = −xx
x
HI
36 rev/h 0ω ω= = = =y zy z
y z
H HI I
COSMOS: Complete Online Solutions Manual Organization System
Vector Mechanics for Engineers: Statics and Dynamics, 8/e, Ferdinand P. Beer, E. Russell Johnston, Jr., Elliot R. Eisenberg, William E. Clausen, David Mazurek, Phillip J. Cornwell © 2007 The McGraw-Hill Companies.
(a) Precession axis:
86.912tan 45.86484.331
θ θ= − = = °x
y
HH
44.1 , 45.9 , 90θ θ θ= ° = ° = °x y z "
43.992tan 50.70536
ωγ γω
= − = = °x
y
4.841γ θ− = °
2 2 56.844 rev/hx yω ω ω= + =
Law of sines
( )sin sin sinφ ψ ω
γ γ θ θ= =
−
! !
(b) 56.844sin 50.705sin 45.864
φ °=°
!
61.3 rev/hφ =! "
(c) 56.844sin 4.841sin 45.864
ψ °=°
!
6.68 rev/hψ =! "