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Illustration of FE algorithm on the example of 1D problem Problem: Stress and displacement analysis of a one-dimensional bar, loaded only by its own weight, acting in the direction of the x-axis Given data: S, L, r , E, g – cross section area, length, material density, - PowerPoint PPT Presentation
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Illustration of FE algorithm on the example of 1D problem
Problem:
Stress and displacement analysis of a one-dimensional bar, loaded only by its own weight, acting in the direction of the x-axis Given data: S, L, , E, g – cross section area, length, material density,
Young’s modulus, gravity acceleration
Fig.1 Problem solved
STEP 1 – MESH GENERATION1D continuum is divided into a set of elements and nodes, according to Fig.2.
Fig.2 FE mesh
STEP 2 – DISPLACEMENT APPROXIMATIONWe concentrate now on the element no.1. Its displacement u(x) is approximated by linear shape functions
Where is the shape function matrix,
matrix of deformation parameters, which have a simple physical interpretation of displacements of mesh nodes - see Fig.3.
Fig.3 Bar element
u x( ) .N
N [ , ]N N1 2
[ , ]u u T1 2
u1 u2
Lp
x1 x2
Linear shape functions
where x1, x2 are the nodal coordinates according to Fig.3.
Displacement of any point of the bar is thus determined by displacement of its nodes
as can be seen in Fig.4
Fig.4 Approximation of displacement
,,12
12
12
21 xx
xxN
xx
xxN
2211 ).().()( uxNuxNxu
STEP 3 – ELEMENT STIFFNESS MATRIXFrom displacements, the approximation of strain and stress can be obtained,
and
where B is the matrix obtained from N by derivation
or ,
if we denote the length of element as .
Inserting stress and strain into the strain energywe obtain after some manipulations
where k is the element stiffness matrix
δBδN .).( dx
d EE TT .... BδδB
]1,1[1
12
xxdx
dNB ]1,1[
1
pLB
12 xxLp
δkδδBBδ ..2
1..
2
1 2
1
1T
x
x
TT dxESW
11
11
pL
ESk
2
1
21
1
x
x
SdxW
STEP 4 – ELEMENT LOAD MATRIX
By analogy, load matrix can be obtained inserting the displacement
approximation into the potential of external forces ,
which results in .
The load matrix represents total external loading of
element (in this particular case its weight), localised into point forces acting in the nodes of the element.
STEP 5 – GLOBAL STIFFNESS AND LOAD MATRIX
Creating global matrix of deformation parameters , strain energy of the 1st element can be written
2
1
1
x
x
dxgSuP
fδ .1TP
1
1
2
1pgSLf
Tuuuu ],,,[ 4321U
UKU ..2
111
TW
where
is the stiffness matrix of the first element, enhanced by zero-element lines and columns to enable multiplication by the matrix U. By the same logic, stiffness matrices of the second and third element can be written as
.
As the total strain energy is a sum of element contributions, we can write it as
,
where K is the global stiffness matrix of the structure
.
0000
0000
0011
0011
1pL
ESK
1100
1100
0000
0000
,
0000
0110
0110
0000
32pp L
ES
L
ESKK
UKUUKKKU ..2
1..
2
13
1321
T
i
TiWW
1100
1210
0121
0011
pL
ESK
By the same procedure, global load matrix F can be obtained as a sum of element contributions to the total potential of external forces :
,
.
STEP 6 – RESULTING SYSTEM OF EQUATIONSUsing previous matrices K, F, total potential energy can be expressed as
From the stationary condition
FUFFFU .. 321
3
1
TT
iiPP
1
2
2
1
2
1pgSLF
FUUKU ...2
1 TT
0U
we obtain the system of four linear algebraic equations for the four deformation
parameters u1, u2, u3, u4 : .
This is the basic equation to be solved. We can see that the stiffness matrix K is the matrix of coefficients. Detailed inspection of our K matrix shows, nevertheless, that it is singular and that the equations have thus no unambiguous solution. This is caused by the fact that we have not specified any boundary condition yet. We should remember a very important fact:
In the static problems of displacement version of FEM, at least so many boundary conditions must be defined to prevent free motion of the analysed model. If this condition is not met, the resulting stiffness matrix is singular and solution of equations usually breaks down.
To meet this condition in our case, we prescribe zero displacement for the first unknown, u1 = 0. This means that from the system of equations we must leave out the first equation, which results in the following form of our global matrices:
FUK .
1
2
2
2
1,,
110
121
012
4
3
2
pp
gSL
u
u
u
L
ES FUK
If we look at the structure of K matrix now, we can see it is a symmetric, positive definite band matrix with dominant diagonal, which is very helpful for quick, stable and efficient computational solution of very large systems of equations.
STEP 7 – SOLUTION OF EQUATIONSSolution of the basic system of equations yields nodal displacements, from which the approximation of element displacement, strain and stress can be obtained according to the equations given above. Figs.5 and 6 show the difference between the analytical and numerical solution of this illustrative example. We should note, that the exact correspondence of numerical and analytical solution in nodal displacements is only a consequence of a very simple problem, it cannot be generalized. Typical for the elements with linear shape functions is, of course, linear approximation of displacements, and constant approximation of stress and strain on elements, with no continuity between elements - see Fig.6.
Analytic solution
FEM
Fig.5 Displacements of bar
Analytic solution
FEM
Fig.6 Stress in the bar