cee 570 finite element methods (in solid and structural...
TRANSCRIPT
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TOTAL : ____________________
University of Illinois at Urbana-Champaign College of Engineering
CEE 570 – Finite Element Methods (in Solid and Structural Mechanics)
Spring Semester 2013
Quiz #1 February 25, 2013
Name: ______SOLUTION__________________ ID#: _____________________
PS.: ALL the pages must be stapled at all times.
PS2.: This is a closed book, closed notes, open minds exam.
Show ALL work on the exam sheets
SCORE:
Problem 1:_______20_______ / 20 points
Problem 2:_______20_______ / 20 points
Problem 3:_______10_______ / 10 points
Problem 4:_______10_______ / 10 points
Problem 5:_______40_______ / 40 points
100 / 100
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Solution)
(a) Gauss
a. Divergence Theorem
dV ds
u u n
b. Numerical Integration (Gauss Quadrature)
1
11
( ),
: Gauss point
: Gauss weigh
n
i i
i
i
i
I d w
w
c. Least Square Method
d. Other contributions: fundamental theorem of algebra, complex numbers, astronomy,
etc.
Problem 1 (20 points total)
Part I (8 points):
(a) The German scientist
shown at the left is Gauss
(prior to the introduction
of the Euro, his photo
used to be on the 10 mark
bill). State the relevance
of his work in the context
of the finite element
method (FEM). Please use
the language of
mathematics when stating
his contributions.
Acknowledgement: This question is similar to the one provided in the practice Quiz. Notice that
Part II of both quizzes are about the DT (Divergence Theorem)!
n
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Problem 1, Part II (12 points):
Use the famous divergence theorem (DT) to prove that (Green’s first identity):
dAvudVvuvu n)(2
where is an arbitrary three dimensional, smooth, bounded domain with boundary and outward
unit normal vector field n, u and v are scalar fields, dV is a differential volume component, dA is a
differential area component, and “ ” denotes the inner product.
Solution)
T
T
, where , , , , , , , , x y z x y zdV dA n n nx y z
φ φ n φ n
T
2 2 2
2 2 2
2
, ,
v v vu v u u u
x y z
u v
v v vu u u
x x x y z z
v v v u v u v u vu
x y z x x y y z z
u v u v
φ
φ
2 ,u v u v dV u v dA
n
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23
12 6
6 4
B
AB
B
ubEI
b bb
k
2
3
12 6 0
6 4 0
0 0 0
B
AB B
C
b uEI
b bb
k
Problem 2, Part I (10 points):
For the plane frame shown below, assume that members are slender and have same EI, and that
axial deformations are negligible in comparison with bending deformations. Let loads and
deformations be confined to the plane of the frame. Write the 3x3 structure stiffness matrix that
operates on the “active” DOFs (degrees of freedom) { } and the corresponding load
vector considering the load P applied at node C, as indicated in the figure below.
Solution)
- Element
P
L
EI
L
EI
L
EI
L
EIL
EI
L
EI
L
EI
L
EIL
EI
L
EI
L
EI
L
EIL
EI
L
EI
L
EI
L
EI
Ke
4626
612612
2646
612612
22
2323
22
2323
Acknowledgment: This problem was
extracted from HW#2, problem 2.5-5.
2 2
3 2 2
4 2
2 4
B
BC
C
a aEI
a a a
k
23
12 6
6 4
B
CD
C
ubEI
b bb
k
2 2
3
2 2
0 0 0
0 4 2
0 2 4
B
zBC B
C
uEI
a ab
a a
k
3
2
12 0 6
0 0 0
6 0 4
B
zCD B
C
b uEI
ab b
k
3 2 2
2
2
24 / 6 / 6 /
6 / 4 / 4 / 2 /
6 / 2 / 4 / 4 /
B
AB BC CD B
C
b b b u
EI b b a a
b a b a
k k k k 0
0
P
P
- Local [ ]
- Global [ ] (all DOFs)
- Load vector
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Problem 2, Part II (10 points):
The spring in the figure below is NONLINEAR and exerts a force proportional to the square of
its stretch. Write the expression for its potential energy and from it determine the equilibrium
value of the displacement .
Solution)
3
0
3
2
3
3
0
/
D
P
Peq
eq
kDU Fdu
PD
kDU PD
dkD P
dD
D P K
u
Pk
F
u
F=ku2
Acknowledgement: This problem was suggested as an OPTIONAL HOMEWORK during the
class of February 6, 2013 – the suggestion can also be found on the file CEE570-ppt10.pdf,
which is available on our class website.
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Problem 3 (10 points):
For the 2D beam element shown below, write the nodal displacement vector {d} that describes a
rigid body rotation of 1800
about node 1. For this vector, verify the product [k]{d}. Is the
resulting vector null or not? Why?
Solution)
The nodal displacement vector {d} T
1 1 1 2 2 2
T
{ } { , , , , , }
{0, 0, 180 , - 2 , 0, 180 )
u v u v
L
d
T
2 2
12 6 12 6{ } 2 , , , 2 , , [null vector]
EI EI EI EIEA EA
L L L L
K d
The resulting vector is not a null vector because rotation of is not small.
1 2
1
2
3 4
5
6 3 2 3 2
2 2
3 2 3 2
2 2
0 0 0 0
12 6 12 60 0
6 4 6 20 0
0 0 0 0
12 6 12 60 0
6 2 6 40 0
EA EA
L L
EI EI EI EI
L L L L
EI EI EI EI
L L L L
EA EA
L L
EI EI EI EI
L L L L
EI EI EI EI
L L L L
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For example, assume rigid body rotation of about node 1.
Displacement vector is
T
1 1 1 2 2 2
T
{ } { , , , , , }
{0, 0, , cos , sin , )
u v u v
L L L
d
Since the characteristic of the rigid body rotation is { } { }K d 0
2 3 2
2
2 3
2
0 0 0
6 12 60
4 6 20
( cos ) sin
0 0
6 120
2 60
EA
L
EI EI EI
L L L
EI EI E
L LL L L
EA
L
EI EI
L L
EI EI
L L
2
0
0
0
00
60
40
I
L
EI
L
EI
L
This work when small (note : sin , cos 1)
𝜃
𝐿 1
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Problem 4 (10 points):
Imagine that a curve φ = φ(x) is to be fitted to three data values: φ1 (actual field quantity) and
φ,x1 (slope of the field quantity) at x=0; and φ2 at x=L. Determine the FEM shape functions.
Hint: you may want to verify the properties of the shape functions to make sure that they are
correct.
Solution)
[ ]{ } [ ] {
}
[ ]{ } [ ] {
}
Evaluate given conditions (let )
{
} [ ] {
} [
] {
}
{
} [ ] { } [
] {
}
Using equation 3.2-3; [ ][ ] { } [ ]{ }, where
[ ] [
(
)
]
[ ] [
]
( ) ( ) ( ) ( )
Acknowledgement: This problem was assigned as part of Homework 2 (Problem 3.2-5). It is
also similar to the interpolation problem assigned in Homework #1 (Problem 1.3-3(c)).
Moreover, Problem 1.3-3(a) was discussed in detail in the Hints for HW#1.
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Problem 5 (40 points):
Consider the quarter of a plate with a hole as in Figure 1. The plate will be modeled using plane
stress, with a thickness of 0.1, a Young’s modulus E of 125 and Poisson ratio of 0.25. A
pressure load of is applied at the right end. The domain is discretized using
elements as in Figure 2. Fill the 14 missing spaces in the ABAQUS input file, and
answer questions (a) through (g). *HEADING
Quarter plate with hole problem - QUIZ 1
*NODE
1, 2.0000, 0.0000
2, 3.0000, 0.0000
3, 4.0000, 0.0000
4, 4.0000, 1.0000
5, 4.0000, 2.0000
6, 4.0000, 3.0000
7, 4.0000, 4.0000
8, 3.0000, 4.0000
9, 2.0000, 4.0000
10, 1.0000, 4.0000
11, 0.0000, 4.0000
12, 0.0000, 3.0000
13, 0.0000, 2.0000
14, 0.7654, 1.8478
15, 1.4142, 1.4142
16, 1.8478, 0.7654
17, 2.7071, 1.7071
18, 1.7071, 2.7071
*ELEMENT, TYPE=CPS8, ELSET=THINPLATE
1, 1, 3, 5, 15, 2, 4, 17, 16
2, 15, 5, 7, 9, 17, 6, 8, 18
3, 13, 15, 9, 11, 14, 18, 10, 12
*SOLID SECTION, ELSET=THINPLATE, MATERIAL=MAT01
0.1
*MATERIAL, NAME=MAT01
*ELASTIC
125, 0.25
*STEP, PERTURBATION
*STATIC
*BOUNDARY
1, 2
2, 2
3, 2
11, 1
12, 1
13, 1
*DLOAD
Figure 1
Figure 2
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1, P2, -3
2, P2, -3
*NODE PRINT
U, RF
*EL PRINT, POSITION=AVERAGED AT NODES
S, E
*END STEP
(a) What is the total size of the full stiffness matrix for the static analysis of the problem?
( )
Size of the full stiffness matrix is then
(b) What is the maximum semi-bandwidth of the stiffness matrix in (a)?
( ) ( ) ( )
The problem will be remodeled using elements. In doing so, the domain is partitioned
into three surfaces and meshed in PATRAN as in Figure 3.
Figure 3: Domain meshed using 3 surfaces with elements each
(c) What is the number of FE nodes after meshing? What is the number of FE nodes after
equivalencing?
After meshing: 27
After equivalencing: Counting the nodes in the "stitched together" so then model nodes = 21
(d) What is the total size of the full stiffness matrix for the static analysis of the problem now
modeled using elements?
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( )
Size of the full stiffness matrix is then
(e) Draw (neatly) the DUAL GRAPH (DG) and the COMMUNICATION GRAPH (CG)
associated to the finite element mesh of Figure 3. Hint: Notice that both DG and CG are
element graphs (not a nodal graph).
(f) Why is plane stress appropriate for this problem?
The plate is thin and out of plane stresses can be considered negligible
DUAL GRAPH COMMUNICATION GRAPH
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(g) The following plot represents for the quarter domain. Clearly mark the stress
concentration point in the plot and briefly explain whether this behavior makes sense or
not.
The hole causes a stress concentration that is maximum around the hole and where the
plate's connecting segment is at its thinnest.