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Finite Element Method
Brian Hammond
Ivan Lopez
Ingrid Sarvis
Fundamental Concept of FEM
• A continuous field of a certain domain
having infinite degrees of freedom is
approximated by a set of piecewise
continuous models with a number of finite
regions called elements. The number of
unknowns defined as nodes are determined
using a given relationship i.e.{F}=[K]*{d}.
Fundamental Concept of FEM
• Red line-Continuous
field over the entire
domain.
• Blue line-Finite
number of linear
approximations with
the finite number of
elements
Domain 
x
x
Domain with degrees of freedom


f
x
f1
f2
f3 f4
f5 f6
x
f Subdomain We
Domain divided with subdomains
with degrees of freedom
General Steps
1) Discretize the domain
a) Divide domain into finite elements using appropriate
element types (1-D, 2-D, 3-D, or Axisymmetric)
2) Select a Displacement Function
a) Define a function within each element using the nodal
values
3) Define the Strain/Displacement and Stress/strain
Relationships
4) Derive the Element Stiffness Matrix and Equations
a)Derive the equations within each element
General Steps
5) Assemble the Element Equations to Obtain the
Global or Total Equations and Introduce
Boundary Conditions
a)Add element equations by method of superposition to
obtain global equation
6) Solve for the Unknown Degrees of Freedom (i.e
primary unknowns)
7) Solve for the Element Strains and Stresses
8) Interpret the Results
Applications
• Stress Analysis
– Truss and frame
analysis
– Stress concentration
• Buckling
• Vibration analysis
• Heat transfer
• Fluid flow
Advantages of FEM
• Model irregularly shaped bodies
• Compute General load conditions
• Model bodies composed of different materials
• Solve unlimited numbers and kinds of boundary
conditions
• Able to use different element sizes in places where
loads or stresses are concentrated
• Handle non-linear behavior using linear
approximations
• Reduce System Cost
FEM Packages
• Large Commercial Programs
– Designed to solve many types of problems
– Can be upgraded fairly easily
– Initial Cost is high
– Less efficient
• Special-purpose programs
– Relatively short, low development costs
– Additions can be made quickly
– Efficient in solving their specific types of problems
– Can’t solve different types of problems
FEM Packages
• Algor
• ANSYS
• COSMOS/M
• STARDYNE
• IMAGES-3D
• MSC/NASTRAN
• SAP90
• GT-STRUDL
Note on Stiffness matrix
For a 1-D bar, the stiffness matrix is derived from the
stress/strain relationship in Hooke’s law and the definitions
of stress and strain.
σx = Eεx. ; σx = P/A ; εx = du/dx = (d2x – d1x)/L
By substitution: -f1x = EA (d2x – d1x)
L
f1x = EA (d1x – d2x)
L
Similarly for f2x: f2x = EA (d2x – d1x)
L
Combining into matrix form, the stiffness matrix is defined
as [k] = EA
L
1 -1
-1 1
f2
f1
d1x d2x
L
A
E
Note on the displacement
function
•For a given set of nodes there exists a function that approximates
the displacement at any position along the bar.
•This function, called the displacement function, is derived from
Pascal’s Triangle.
•A new constant is introduced into the function for every node in
the discretized domain.
u(x) = a1 + a2x + a3x2
+ …
For 1-D
Note on the displacement function
If a 1-D bar is broken into 2 elements, the displacement function
would be u(x) = a1 + a2x + a3x2
.
Putting it into matrix notation: u(x) = [1 x x2
] a1
a2
a3
By knowing the distances to the nodes
and the displacements at those nodes, the
equation becomes: u1
u2
u3
=
1 0 0
1 x2 x2
2
1 x3 x3
2
a1
a2
a3
, where
x1 = 0, x2 and x3 are the distances to the nodes and u1, u2, and u3 are the displacements.
The coefficients are found by solving the equation.
Example
A A
L L
E 2E
P
Determine displacements of materials a and b if
the load P is applied to the end of the bar given
the above information.
a b
Example con’t.
1) Discretize the domain with appropriate elements.
Element a
1 2
Element b
2 3
u1 u2
u2 u3
1 2 3
u1 u2 u3
f3 = P
f1
f1 f3 = P
f21 f22
Example con’t.
2) Select a displacement function
There will be new term for each element, and the terms are
1 2 3
u1 u2 u3
u(x) = a1 + a2x + a3x2
derived from Pascal’s triangle.
Example con’t.
3) Define stress/displacement and stress/strain relationships
σx = Eεx εx = du/dx
4) Derive the element stiffness matrix and element equations
{F} = [k]{d} [k] = stiffness matrix
[k] = EA
L
1 -1
-1 1
{F} = Force
{d} = displacement
f1
f21
= L
1 -1
-1 1
EA u1
u2
f22
f3
= L
2 -2
-2 2
EA u2
u3
,
a b
Example con’t.
5) Construct Global equation and introduce boundary
conditions and known variables.
f1
f21+f22
f3
=
L
1 -1 0
-1 3 -2
0 -2 2
EA u1
u2
u3
Global Equation
B.C.: (x =0) u1 = 0
Known variables: f3 = P and f2 = f21+f22 = 0
Example con’t.
6) Solve for unknowns.
f1
0
P
=
L
1 -1 0
-1 3 -2
0 -2 2
EA 0
u2
u3
f1 = -EAu2
L
0 = EA(3u2-2u3)
L
P = EA(2u3-2u2)
L
u2 = PL
EA
u3 = 3PL
2EA
f1 = -P
Example con’t.
7) Solve for the element strains and stresses.
εa = P = u2
EA L
σa = Eεa = P
A
εb = 3P = u3
2EA L
σa = 2E εb = P
3 A
8) Interpret the Results
•After solving for the displacements, the coefficients of the
displacement function can be determined.
Bibliography
• Logan, Daryl L. A First Course in the
Finite Element Method Using Algor.
Brooks/Cole, Pacific Grove, CA. 2001
• http://www.finite-element-method.info
• http://www.eng.fsu.edu/~chandra/courses/e
ml4536/
• http://urbana.mie.uc.edu/yliu/FEM-525/
FEM_Lecture_Notes_Liu_UC.pdf

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Finite_Element_Method_FULL_FULL_FULL.ppt

  • 1. Finite Element Method Brian Hammond Ivan Lopez Ingrid Sarvis
  • 2. Fundamental Concept of FEM • A continuous field of a certain domain having infinite degrees of freedom is approximated by a set of piecewise continuous models with a number of finite regions called elements. The number of unknowns defined as nodes are determined using a given relationship i.e.{F}=[K]*{d}.
  • 3. Fundamental Concept of FEM • Red line-Continuous field over the entire domain. • Blue line-Finite number of linear approximations with the finite number of elements Domain  x x Domain with degrees of freedom   f x f1 f2 f3 f4 f5 f6 x f Subdomain We Domain divided with subdomains with degrees of freedom
  • 4. General Steps 1) Discretize the domain a) Divide domain into finite elements using appropriate element types (1-D, 2-D, 3-D, or Axisymmetric) 2) Select a Displacement Function a) Define a function within each element using the nodal values 3) Define the Strain/Displacement and Stress/strain Relationships 4) Derive the Element Stiffness Matrix and Equations a)Derive the equations within each element
  • 5. General Steps 5) Assemble the Element Equations to Obtain the Global or Total Equations and Introduce Boundary Conditions a)Add element equations by method of superposition to obtain global equation 6) Solve for the Unknown Degrees of Freedom (i.e primary unknowns) 7) Solve for the Element Strains and Stresses 8) Interpret the Results
  • 6. Applications • Stress Analysis – Truss and frame analysis – Stress concentration • Buckling • Vibration analysis • Heat transfer • Fluid flow
  • 7. Advantages of FEM • Model irregularly shaped bodies • Compute General load conditions • Model bodies composed of different materials • Solve unlimited numbers and kinds of boundary conditions • Able to use different element sizes in places where loads or stresses are concentrated • Handle non-linear behavior using linear approximations • Reduce System Cost
  • 8. FEM Packages • Large Commercial Programs – Designed to solve many types of problems – Can be upgraded fairly easily – Initial Cost is high – Less efficient • Special-purpose programs – Relatively short, low development costs – Additions can be made quickly – Efficient in solving their specific types of problems – Can’t solve different types of problems
  • 9. FEM Packages • Algor • ANSYS • COSMOS/M • STARDYNE • IMAGES-3D • MSC/NASTRAN • SAP90 • GT-STRUDL
  • 10. Note on Stiffness matrix For a 1-D bar, the stiffness matrix is derived from the stress/strain relationship in Hooke’s law and the definitions of stress and strain. σx = Eεx. ; σx = P/A ; εx = du/dx = (d2x – d1x)/L By substitution: -f1x = EA (d2x – d1x) L f1x = EA (d1x – d2x) L Similarly for f2x: f2x = EA (d2x – d1x) L Combining into matrix form, the stiffness matrix is defined as [k] = EA L 1 -1 -1 1 f2 f1 d1x d2x L A E
  • 11. Note on the displacement function •For a given set of nodes there exists a function that approximates the displacement at any position along the bar. •This function, called the displacement function, is derived from Pascal’s Triangle. •A new constant is introduced into the function for every node in the discretized domain. u(x) = a1 + a2x + a3x2 + … For 1-D
  • 12. Note on the displacement function If a 1-D bar is broken into 2 elements, the displacement function would be u(x) = a1 + a2x + a3x2 . Putting it into matrix notation: u(x) = [1 x x2 ] a1 a2 a3 By knowing the distances to the nodes and the displacements at those nodes, the equation becomes: u1 u2 u3 = 1 0 0 1 x2 x2 2 1 x3 x3 2 a1 a2 a3 , where x1 = 0, x2 and x3 are the distances to the nodes and u1, u2, and u3 are the displacements. The coefficients are found by solving the equation.
  • 13. Example A A L L E 2E P Determine displacements of materials a and b if the load P is applied to the end of the bar given the above information. a b
  • 14. Example con’t. 1) Discretize the domain with appropriate elements. Element a 1 2 Element b 2 3 u1 u2 u2 u3 1 2 3 u1 u2 u3 f3 = P f1 f1 f3 = P f21 f22
  • 15. Example con’t. 2) Select a displacement function There will be new term for each element, and the terms are 1 2 3 u1 u2 u3 u(x) = a1 + a2x + a3x2 derived from Pascal’s triangle.
  • 16. Example con’t. 3) Define stress/displacement and stress/strain relationships σx = Eεx εx = du/dx 4) Derive the element stiffness matrix and element equations {F} = [k]{d} [k] = stiffness matrix [k] = EA L 1 -1 -1 1 {F} = Force {d} = displacement f1 f21 = L 1 -1 -1 1 EA u1 u2 f22 f3 = L 2 -2 -2 2 EA u2 u3 , a b
  • 17. Example con’t. 5) Construct Global equation and introduce boundary conditions and known variables. f1 f21+f22 f3 = L 1 -1 0 -1 3 -2 0 -2 2 EA u1 u2 u3 Global Equation B.C.: (x =0) u1 = 0 Known variables: f3 = P and f2 = f21+f22 = 0
  • 18. Example con’t. 6) Solve for unknowns. f1 0 P = L 1 -1 0 -1 3 -2 0 -2 2 EA 0 u2 u3 f1 = -EAu2 L 0 = EA(3u2-2u3) L P = EA(2u3-2u2) L u2 = PL EA u3 = 3PL 2EA f1 = -P
  • 19. Example con’t. 7) Solve for the element strains and stresses. εa = P = u2 EA L σa = Eεa = P A εb = 3P = u3 2EA L σa = 2E εb = P 3 A 8) Interpret the Results •After solving for the displacements, the coefficients of the displacement function can be determined.
  • 20. Bibliography • Logan, Daryl L. A First Course in the Finite Element Method Using Algor. Brooks/Cole, Pacific Grove, CA. 2001 • http://www.finite-element-method.info • http://www.eng.fsu.edu/~chandra/courses/e ml4536/ • http://urbana.mie.uc.edu/yliu/FEM-525/ FEM_Lecture_Notes_Liu_UC.pdf