FEM - solution of nonlinear problems
Jerzy Pamin e-mail: JPamin@L5.pk.edu.pl
With thanks to:
A. Wosatko, A. Winnicki
ADINA R&D, Inc.http://www.adina.com ANSYS, Inc. http://www.ansys.com TNO DIANA http://www.tnodiana.com
Lecture scope
Nonlinear problems Geometrical nonlinearity Physical nonlinearity Cracking
Final remarks References
[1] R. de Borst and L.J. Sluys. Computational Methods in Nonlinear Solid Mechanics. Lecture notes, Delft University of Technology, 1999.
[2] G. Rakowski, Z. Kacprzyk. Metoda elementow skończonych w mechanice kostrukcji. Oficyna Wyd. PW, Warszawa, 2005.
[3] M. Jir´asek and Z.P. Baˇzant. Inelastic Analysis of Structures. J. Wiley &
Sons, Chichester, 2002.
[4] M. Kwasek Advanced static analysis and design of reinforced concrete deep beams. Diploma work, Politechnika Krakowska, 2004.
Nonlinearity sources
Caused by change of geometry of (deformable) body
I large strains (e.g. rubber, metal forming)
I large displacements (e.g. slender, thin-walled structures)
I contact (interaction of bodies in contact)
I follower load (varying with deformation) Caused by nonliear constitutive relations
I plasticity (irreversible strains)
I damage (degradation of elastic properties)
I fracture (continuous representation of cracks)
I . . . Remarks:
I Superposition principle does not hold.
I It is possible to describe discontinuum in which components are connected by interfaces (e.g. composite structures) or (discrete) cracks occur. The interfaces usually have nonlinear features which represent for instance friction, adhesion, cracking.
Nonlinear continuum [1,2,3]
Equilibrium equations + static boundary conditions LTσ + b = 0 w V , σν = ˆt na S where:
L – differential operator matrix
σ – tensor/vector of generalized stresses b – body force vector
ν
V S ˆt
Weak form of equilibrium equations Z
V
δuT(LTσ + b) dV = 0 ∀δu
Virtual work principle δWint = δWext
Z
V
(Lδu)Tσ dV = Z
V
δuTb dV + Z
S
δuTˆt dS
Galerkin method
Displacement-based finite elements
u ≈ uh=
nw
X
i =1
Ni(ξ, η, ζ)ui= Nde
where: N - shape function matrix, de - element vector of degrees of freedom (dofs),
nw - number of nodes
Transformation of nodal degrees of freedom de = Aed where: d - global vector of dofs
Weak form of equilibrium for discretized system
ne
X
e=1
Ae T Z
Ve
BTσ dV = fext, B = LN
Isoparametric approach, numerical integration
Linear elasticity
Hooke’s law
Tensor notation: σ = De : , σij = Dijkle kl
Matrix notation:
σ = De, σ =
σx
σy
σz
τxy
τyz
τzx
, =
x
y
z
γxy
γyz
γzx
Material isotropy: De= De(E , ν)
E 1
σ
loading unloading
Linear kinematic equations
Tensor notation: = 12[∇u + (∇u)T], ij =12(ui ,j+ uj ,i) Matrix notation: = Lu
Hence stress tensor: σ = De = DeLu = DeLNde = DeBAed Equilibrium equations for discretized system
ne
X
e=1
Ae T Z
Ve
BTDeB dV Aed = fext, Kd = fext
Incremental-iterative analysis
Nonlinear problem:
fext applied in increments
t → t + ∆t → σt+∆t= σt+ ∆σ Equilibrium at time t + ∆t:
ne
X
e=1
Ae T Z
Ve
BTσt+∆tdV = fextt+∆t
ne
X
e=1
Ae T Z
Ve
BT∆σ dV = fextt+∆t− fintt where: fintt =Pne
e=1Ae TR
VeBTσtdV Linearization of the left-hand side at time t
∆σ = ∆σ(∆(∆u)) Equation set for an increment:
K ∆d = fextt+∆t− fintt
Algorithm of incremental-iterative method
Iterative corrections necessary in order to reach equilibrium at time t + ∆t → Newton-Raphson algorithm
Out-of-balance (residual) forces: Rj = fextt+∆t− fint,jt+∆t→ 0 f
R1
fint,1
u ut+∆t
ut fextt fextt+∆t
∆u1 du2
∆fext
K ∆d = fextt+∆t− fintt
K- tangent operator First iteration:
∆d1=K−10 (fextt+∆t− fintt ) σ1 → fint,1t+∆t6= fextt+∆t Corrections:
ddj +1= K−1j (fextt+∆t−fint,jt+∆t) σj +1 → fint,j +1t+∆t
Convergence criterion:
kft+∆text −ft+∆t int,j k k∆fextk ¬ δ Modified algorithm:
Kj= K0
Algorithm of incremental-iterative method
Iterative corrections necessary in order to reach equilibrium at time t + ∆t → Newton-Raphson algorithm
Out-of-balance (residual) forces: Rj = fextt+∆t− fint,jt+∆t→ 0 f
R1
fint,1
u ut+∆t
ut fextt fextt+∆t
∆u1 du2
∆fext
K ∆d = fextt+∆t− fintt
K - tangent operator First iteration:
∆d1= K−10 (fextt+∆t− fint,0t+∆t) σ1 → fint,1t+∆t6= fextt+∆t Corrections:
ddj +1= K−1j (fextt+∆t−fint,jt+∆t) σj +1 → fint,j +1t+∆t
Convergence criterion:
kft+∆text −ft+∆t int,j k k∆fextk ¬ δ Modified algorithm:
Kj= K0
Algorithm of incremental-iterative method
Iterative corrections necessary in order to reach equilibrium at time t + ∆t → Newton-Raphson algorithm
Out-of-balance (residual) forces: Rj = fextt+∆t− fint,jt+∆t→ 0 f
R1
fint,1
u ut+∆t
ut fextt fextt+∆t
∆u1 du2
∆fext
Kjdd = fextt+∆t− fint,jt+∆t K - tangent operator First iteration:
∆d1= K−10 (fextt+∆t− fint,0t+∆t) σ1 → fint,1t+∆t6= fextt+∆t Corrections:
ddj +1= K−1j (fextt+∆t−fint,jt+∆t) σj +1 → fint,j +1t+∆t
Convergence criterion:
kft+∆text −ft+∆t int,j k k∆fextk ¬ δ Modified algorithm:
Kj= K0
Algorithm of incremental-iterative method
Iterative corrections necessary in order to reach equilibrium at time t + ∆t → Newton-Raphson algorithm
Out-of-balance (residual) forces: Rj = fextt+∆t− fint,jt+∆t→ 0 f
u ut+∆t
ut fextt fextt+∆t
∆u1 du2
∆fext
R2
fint,2
Kjdd = fextt+∆t− fint,jt+∆t K - tangent operator First iteration:
∆d1= K−10 (fextt+∆t− fint,0t+∆t) σ1 → fint,1t+∆t6= fextt+∆t Corrections:
ddj +1= K−1j (fextt+∆t−fint,jt+∆t) σj +1 → fint,j +1t+∆t
Convergence criterion:
kft+∆text −ft+∆t int,j k k∆fextk ¬ δ Modified algorithm:
Kj= K0
Options of incremental loading control
Force or displacement control
Arc length control
Geometrical nonlinearity
X
u
x φ(X, t)
V V0
S S0
x1, X1
x2, X2
Initial and current configuration Motion function: x = φ(X, t)
Displacement vector: u(X, t) = x − X
Deformation gradient (main deformation measure): F = ∂φ∂X= ∇Xx Strain tensor (one of possible strain measure):
E = 1
2(FTF − I) = 1
2[∇Xu + (∇Xu)T+ (∇Xu)T∇Xu]
Geometrical nonlinearity
Nonlinear kinematic equations, e.g. εx = εLx+εNx =∂u∂x +12 ∂w∂x2
∆σ = ∆σ(∆(∆u))
I Balance equations describe the equilibrium of deformed body. The virtual work principle can be written for the initial or current configuration.
I Different stress measures are associated with different strain measures.
I Small strains: E ≈ = 12[∇u + (∇u)T] < 2%.
I Small displacements (and rotations): V ≈ V0(one description, equilibrium equations for undeformed configuration).
Geometrical nonlinearity
Equilibrium of discretized system [4]:
K ∆d = fextt+∆t− fintt
where tangent stiffness matrix:
K = K0+Ku+Kσ
K0- linear stiffness matrix Ku - initial displacement matrix
(discrete kinematic relations matrix B dependent on displacements) Kσ - initial stress matrix (dependent on generalized stresses)
Physical nonlinearity
K ∆d = fextt+∆t− fintt Linearization of LHS at time t:
∆σ =∆σ(∆(∆u))
∆σ = ∂σ∂t ∂
∂u
t
∆u D =∂σ∂, L = ∂∂u
Discretization: ∆u = N∆de
Linear geometrical relations → Matrix of discrete kinematic relations B = LN independent of displacements
Tangent stiffness matrix
K =
ne
X
e=1
Ae T Z
Ve
BTDB dV Ae
Plastic yielding of material
A B C
displacement force
P
A
+
-
σy
σy
σy
σy
σy
σy
+
- -
+ C B
elastic material
equivalent plastic strain distribution plastified
elastic material
Discrete and smeared cracks
Fracture energy Gf (used to create unit surface area of a crack)
Simulation of cracking in RC panel
with ATENA [4]
Final remarks
1. Computer simulations offer priceless possibilities, but should be performed only by conscious FEM users.
2. Three-dimensional (3D) modelling starts to dominate in prediction of nonlinear behaviour of structures.
3. Consistent linearization of equations guarantees quadratic convergence of Newton-Raphson algorithm.
4. In order to improve the quality of FEM approximation adaptive mesh refinenment based on evaluation of discretization error is advisable.