strength of material chapter 5
TRANSCRIPT
PPB 25403 Strength of
Materials
Lecture 5: Torsion
Learning Outcomes
Torsion twisting of an object due to an applied torque
Torsional Deformation of Circular Shaft
Torsion Formula
Angle of Twist
Transmission of Power
Torsional Deformation of a Circular Shaft
Torque is a moment that twists a member about its
longitudinal axis.
If the angle of rotation is small, the length of the shaft
and its radius will remain unchanged.
The Torsion Formula
When material is linear-elastic, Hooke’s law applies.
A linear variation in shear strain leads to a
corresponding linear variation in shear stress
along any radial line on the cross section.
J
Tp
J
Tcor max
= maximum shear stress in the shaft
= shear stress
= resultant internal torque
= polar moment of inertia of cross-sectional area
= outer radius of the shaft
= intermediate distance
max
TJc
p
The Torsion Formula
If the shaft has a solid circular cross section,
If a shaft has a tubular cross section,
4
2cJ
44
2io ccJ
Example 5.2The solid shaft of radius c is subjected to a torque T. Find the fraction of T that is
resisted by the material contained within the outer region of the shaft, which has an
inner radius of c/2 and outer radius c.
Solution:
dcdAdT 2' max
maxc
For the entire lighter-shaded area the torque is
(1) 32
152' 3
max
2/
3max cdc
T
c
c
Stress in the shaft varies linearly, thus
The torque on the ring (area) located within
the lighter-shaded region is
Using the torsion formula to determine the maximum stress in the shaft, we have
Solution:
(Ans) 16
15' TT
3max
4max
2
2
c
T
c
Tc
J
Tc
Substituting this into Eq. 1 yields
Example 5.3The shaft is supported by two bearings and is subjected to three torques. Determine
the shear stress developed at points A and B, located at section a–a of the shaft.
Solution:From the free-body diagram of the left segment,
mm 1097.4752
74J
kNmm 1250030004250 ;0 TTM x
The polar moment of inertia for the shaft is
Since point A is at ρ = c = 75 mm,
(Ans) MPa 89.11097.4
7512507J
TcB
Likewise for point B, at ρ =15 mm, we have
(Ans) MPa 377.01097.4
1512507J
TcB
Power Transmission
Power is defined as the work performed per unit of
time.
For a rotating shaft with a torque, the power is
Since , the power equation is
For shaft design, the design or geometric parameter
is
dtdTP / locity,angular veshaft where
f2rad 2cycle 1
fTP 2
allow
T
c
J
Example 5.5A solid steel shaft AB is to be used to transmit 3750 W from the motor M to which it
is attached. If the shaft rotates at w =175 rpm and the steel has an allowable shear
stress of allow τallow =100 MPa, determine the required diameter of the shaft to the
nearest mm.
Solution:The torque on the shaft is
Nm 6.20460
21753750 TT
TP
Since
mm 92.10100
10006.20422
2
3/13/1
4
allow
allow
Tc
T
c
c
c
J
As 2c = 21.84 mm, select a shaft having a diameter of 22 mm.
Angle of Twist
Integrating over the entire length L of the shaft, we have
Assume material is homogeneous, G is constant, thus
Sign convention is
determined by right hand rule,
L
GxJ
dxxT
0
Φ = angle of twist
T(x) = internal torque
J(x) = shaft’s polar moment of inertia
G = shear modulus of elasticity for the material
JG
TL
Example 5.8The two solid steel shafts are coupled together using the meshed gears. Determine
the angle of twist of end A of shaft AB when the torque 45 Nm is applied. Take G to
be 80 GPa. Shaft AB is free to rotate within bearings E and F, whereas shaft DC is
fixed at D. Each shaft has a diameter of 20 mm.
Solution:From free body diagram,
Nm 5.22075.0300
N 30015.0/45
xDT
F
Angle of twist at C is
rad 0269.01080001.02
5.15.2294
JG
TLDCC
Since the gears at the end of the shaft are in mesh,
rad 0134.0075.00269.015.0B
Solution:
Since the angle of twist of end A with respect to end B of shaft AB caused by the
torque 45 Nm,
rad 0716.01080010.02
24594/
JG
LT ABABBA
The rotation of end A is therefore
(Ans) rad 0850.00716.00134.0/ BABA
Example 5.10The tapered shaft is made of a material having a shear modulus G. Determine the
angle of twist of its end B when subjected to the torque.
Solution:From free body diagram, the internal torque is T.
L
ccxcc
x
cc
L
cc 122
212
Thus, at x,
4
122
2 L
ccxcxJ
For angle of twist,
(Ans) 3
223
2
3
1
2
121
2
2
0
4
122
cc
cccc
G
TL
L
ccxc
dx
G
TL
Example 5.11The solid steel shaft has a diameter of 20 mm. If it is subjected to the two torques,
determine the reactions at the fixed supports A and B.
Solution:By inspection of the free-body diagram,
(1) 0500800 ;0 Abx TTM
Since the ends of the shaft are fixed, 0/ BA
Using the sign convention,
(2) 7502.08.1
03.05.15002.0
BA
AAB
TT
JG
T
JG
T
JG
T
Solving Eqs. 1 and 2 yields TA = -345 Nm and TB = 645 Nm.
Solid Noncircular Shafts
The maximum shear stress and the angle of twist for
solid noncircular shafts are tabulated as below:
Example 5.13The 6061-T6 aluminum shaft has a cross-sectional area in the shape of an
equilateral triangle. Determine the largest torque T that can be applied to the end of
the shaft if the allowable shear stress is τallow = 56 MPa and the angle of twist at its
end is restricted to Φallow = 0.02 rad. How much torque can be applied to a shaft of
circular cross section made from the same amount of material? Gal = 26 GPa.
Solution:By inspection, the resultant internal torque at any cross section
along the shaft’s axis is also T.
(Ans) Nm 12.24102640
102.146.020 ;
46
Nm 2.177940
2056 ;
20
34
3
4
33
TT
Ga
T
TT
a
T
al
allow
allow
By comparison, the torque is limited due to the angle of twist.
Solution:
(Ans) Nm 10.33102685.142/
102.102.0 ;
Nm 06.28885.142/
85.1456 ;
34
3
4
TT
JG
TL
TT
J
Tc
al
allow
allow
For circular cross section, we have
mm 85.1460sin40402
1c ; 2 cAA trianglecircle
The limitations of stress and angle of twist then require
Again, the angle of twist limits the applied torque.
Thin-Walled Tubes Having Closed Cross Sections
Shear flow q is the product of the tube’s thickness and
the average shear stress.
Average shear stress for thin-walled tubes is
For angle of twist,
tq avg
m
avgtA
T
2
τavg = average shear stress
T = resultant internal torque at the cross section
t = thickness of the tube
Am = mean area enclosed boundary
t
ds
GA
TL
m
24
Example 5.14Calculate the average shear stress in a thin-walled tube having a circular cross
section of mean radius rm and thickness t, which is subjected to a torque T. Also,
what is the relative angle of twist if the tube has a length L?
Solution:The mean area for the tube is
2
mm rA
For angle of twist,
(Ans) 22 2
mm
avgtr
T
tA
T
(Ans) 24 32 Gtr
TL
t
ds
GA
TL
mm
Example 5.16A square aluminum tube has the dimensions. Determine the average shear stress in
the tube at point A if it is subjected to a torque of 85 Nm. Also compute the angle of
twist due to this loading. Take Gal = 26 GPa.
Solution:By inspection, the internal resultant torque is T = 85 Nm.
(Ans) N/mm 7.12500102
1085
2
23
m
avgtA
T
For average shear stress,
22 mm 250050mAThe shaded area is
Solution:
dsds
t
ds
GA
TL
m
1-4
32
33
2mm 10196.0
10102625004
105.11085
4
For angle of twist,
Integral represents the length around the centreline boundary of the tube, thus
(Ans) rad 1092.350410196.0 34
Stress Concentration
Torsional stress concentration factor, K, is used to
simplify complex stress analysis.
The maximum shear stress is then determined from the
equation
J
TcKmax
Example 5.18The stepped shaft is supported by bearings at A and B. Determine the maximum
stress in the shaft due to the applied torques. The fillet at the junction of each shaft
has a radius of r = 6 mm.
Solution:By inspection, moment equilibrium about the axis
of the shaft is satisfied
15.0202
6 ;2
202
402
d
r
d
D
(Ans) MPa 10.3020.02
020.0303.1
4maxJ
TcK
The stress-concentration factor can be determined
by the graph using the geometry,
Thus, K = 1.3 and maximum shear stress is
Inelastic Torsion
Considering the shear stress acting on an element of
area dA located a distance p from the center of the
shaft,
Shear–strain distribution over a radial line on a shaft is
always linear.
Perfectly plastic assumes the shaft will continue to twist
with no increase in torque.
It is called plastic torque.
dTA
2
2
Example 5.20A solid circular shaft has a radius of 20 mm and length of 1.5 m. The material has an
elastic–plastic diagram as shown. Determine the torque needed to twist the shaft Φ
= 0.6 rad.
Solution:The maximum shear strain occurs at the surface of
the shaft,
rad 008.002.0
5.16.0 ; max
maxL
mm 4m 004.0008.0
02.0
0016.0Y
Y
Based on the shear–strain distribution, we have
The radius of the elastic core can be obtained by
(Ans) kNm 25.1004.002.046
10754
6
336
33
YY cT