stress constrained topology optimization for … · topology optimization is mostly based on...
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STRESS CONSTRAINED TOPOLOGY OPTIMIZATION FOR ADDITIVE
MANUFACTURING: SPECIFIC CHARACTER AND SOLUTION ASPECTS
Pierre DUYSINX*, Maxime COLLET*, Simon BAUDUIN*,
and Matteo BRUGGI+
* Aerospace and Mechanical Engineering Dept, University of Liege, Belgium
+ Dept of Civil and Environmental Engineering, Politecnico di Milano, Italy
1 ESMC2015 9th European Solid Mechanics Conference,
Madrid, July 6-10, 2015
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OUTLINE
Introduction & Motivation
Topology problem formulation – Problem statement
Specific character of stress constrained design
– Energy vs von Mises stress – Local stress constraints – Unequal stress limits – Fatigue constraints
Large scale optimization
– Sensitivity analysis – Dual optimization algorithms
Conclusion & Perspectives
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INTRODUCTION & MOTIVATION
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MOTIVATION
TOPOLOGY OPTIMIZATION: a creative design tool
ADDITIVE MANUFACTURING
new way of making things
4
Courtesy of ALTAIR and AIRBUS
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INTRODUCTION
Topology optimization is mostly based on compliance design formulation
Many aerospace and mechanical components are designed with respect to strength or fatigue constraints
Need for efficient approaches to handle efficiently stress constrained problems
Extending the scope of stress constrained topology optimization to cope with:
– Fatigue constraints
– Industrial applications Large scale problems
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INTRODUCTION
This paper
– Draws a state-of-the-art of topology optimization of continuum structures with stress constraints
– Illustrates the specific character of maximum strength with respect to compliance design when considering
Several load cases
Different stress limits in tension and compression
– Extends the scope of stress constrained topology optimization to unequal stress constraints, fatigue problems..
– Draws the challenges to tackle large scale optimization problems related to local constraints
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TOPOLOGY OPTIMIZATION FORMULATION
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TOPOLOGY OPTIMIZATION PROBLEM
Optimal material distribution within a given domain
Discretization of displacements and density distribution using FEM
Interpolation of material properties between void and solid and penalize intermediate densities (SIMP model)
Solve optimization problem using efficient MP optimizers with continuous variables
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TOPOLOGY OPTIMIZATION
Density filter:
Implementation : Topology optimization tool in MATLAB based 88-line code by Andreassen et al. (2011)
MMA solver by Svanberg (1987)
9
m i n f 0 ( x ) + z +
P m
j = 1 ( c j y j +
1 2 d j y
2 j )
s . t . : f j ( x ) ¡ a j z ¡ y j · 0 j = 1 : : : m
x i · x i · x i i = 1 : : : n
y j ¸ 0 j = 1 : : : m
z ¸ 0
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TOPOLOGY OPTIMIZATION PROBLEM
Compliance design
– Usual approach
– Unable to capture the specific character of stress constraints
Stress constrained design
– Technical difficulties to be solved
– Define appropriate failure criterion
– Computational effort compared to compliance design 10
[Duysinx et Bruggi (2012)]
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TOPOLOGY OPTIMIZATION
Challenges of stress constraints in topology optimization
– Definition of relevant stress criteria at microscopic level
Microscopic stress should be considered
– Stress singularity phenomenon:
e-relaxation (Chang and Guo, 1992)
q-p relaxation (Bruggi, 2008)
– Large scale optimization problem
Local constraints
Aggregation of constraints: P-norm
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SPECIFIC CHARACTER OF STRESS CONSTRAINTS
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SPECIFIC CHARACTER OF STRESS CONSTRAINTS
Bound of integrated von Mises stress by compliance Bendsoe, Diaz
and Kikuchi (1993)
For single load case and minimum compliance with volume constraint :
– Minimizing strain energy bounds almost everywhere the von Mises stress
– Relation between energy minimization and fully stressed design nearly every where in the material
– Compliance design is efficient to predict optimal structural lay-out
2 3 3:
4(1 ) 4(1 )
T
VM
E Ed C d F U
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SPECIFIC CHARACTER OF STRESS CONSTRAINTS
Local strain energy can be written as (Timoshenko and Goodier, 1970)
– with
Minimizing von Mises stress does not control compressibility energy!!!
Tri-axiality is important.
Stiffness and strength designs can be different when
– Several load cases
– Several materials
– Different stress limits in tension and compression
– Geometrical constraints (perimeter, manufacturing constraints...)
1 2 3
1 2 2 3 3 1
3 3(1 )
1. ( )² ( )² ( )²3 2(1 )
oct
oct
E
EG
2 21 3
2 4
oct octuG
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NUMERICAL APPLICATIONS: 3-BAR TRUSS
Famous benchmark problem with 3 independent load cases
F1 = 40 N
F2 = 30 N
F3 = 20 N
Material and geometrical data
L=1 m
W = 2.5 m
E = 100 N/m²
= 0.3
l = 150 N/m²
Vmax = 25%
Finite Element mesh
50 x 20 finite elements
15
Design variables: 1000
Load cases: 3
Stress constraints: 3000
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NUMERICAL APPLICATIONS: 3-BAR TRUSS
Minimum compliance design
Compliance (1,2,3) = 73.3 Nm
Max von Mises:
1) 229 N/m²
2) 571 N/m²
3) 555 N/m²
Volume = 25%
Stress constrained design
Compliance
1) 91.2 Nm
2) 45.6 Nm
3) 45.0 Nm
Max Von Mises (1,2,3)= 150N/m²
Volume = 26.4 %
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Unequal stress limits in tension and compression
Extending Von Mises criterion to other failure criteria to cope with unequal stress limits behaviors (T C, s=C/T)
Raghava criterion (parabolic criterion from Tsai-Wu criterion family)
Ishai criterion (hyperbolic criterion from Prager-Drucker family)
– with
2 2
1 1 2( 1) ( 1) 12
2
Deq
RAG
J s J s J sT
s
2 1( 1) 3 ( 1)
2
Deq
ISH
s J s JT
s
1 iiJ 2 0.5D ij ijJ s s
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NUMERICAL APPLICATIONS: 3-BAR TRUSS
High compressive strength (s=C/T=3):
(C=450 N/m², T=150 N/m²)
Volume = 25.6 %
Compliance (1,2,3): 92.8, 47,3, 46,0 N*m
High tensile strength (s=C/T=1/3):
(C=150 N/m², T=450 N/m²):
Volume = 12.4 %
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FATIGUE (UNI AXILAL CASE)
Wöhler’s curve : fundamental work
– Reduction of the amplitude of
stress with the number of cycles
Goodman diagram:
– Influence of mean and alternate stress components
– Line of equal failure probability for a certain number of cycles
Amplitude / mean stress
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MULTI AXIAL FATIGUE CRITERIA
Like in 1-D problem let’s assume that the total stress is given by a certain amount of alternate component ca a and a given amount of mean component cm m :
In the following, let assume that alternate and mean components are defined by the same reference load case.
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MULTI AXIAL FATIGUE CRITERIA: SINES
Sines fatigue criterion:
– Where
– With t-1, the fatigue limit in reverse torsion and f0 is the fatigue in repeated bending
For plane stress
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MULTI AXIAL FATIGUE CRITERIA: CROSSLAND
Crossland fatigue criterion is very similar to Sines criterion:
Difference lies in the fact in Crossland the hydrostatic term is evaluated on the basis of the maximum stress (not only on the mean component): max = a + m:
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MULTI AXIAL FATIGUE CRITERIA: SINES
Assuming a SIMP model, after Finite Element discretization:
Considering the micro stresses after applying the polarization factor
The expression Sines criterion for topology optimization reads
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NUMERICAL APPLICATION: L-SHAPE
SIMP model
– Penalization p=3
– q-p relaxation: q=2.6 2.75
Load F=95 N
– ca = 0.7 and cm = 0.3
Material : Steel with properties from Norton (2000)
– E = 1 Mpa (normalized), =0.3
– f = 580 MPa, t-1= 160 MPa, f-1= 260 MPa
Compliance regularization constraint: ac=2
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NUMERICAL APPLICATION: LSHAPE
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Optimal design with Sines criterion Optimal design with Crossland criterion
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NUMERICAL APPLICATION: LSHAPE
26
Stress map for optimal design with Sines criterion
Stress map for optimal design with Crossland criterion
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NUMERICAL APPLICATION: LSHAPE
27 Evolution of the number of active constraints
Evolution of the objective function volume
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SOLVING LARGE SCALE OPTIMIZATION PROBLEMS
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SOLVING LARGE SCALE OPTIMIZATION
Classical strategy: solve optimization sequential convex programming
– Generate first order approximation sub-problems: CONLIN (Fleury, 1985) or MMA (Svanberg, 1987) or GCMMA approximation (Bruyneel et al., 2002)
– Dual solver (Lagrangian maximization)
When dealing with stress constrained design, one hits the limitation of currently available standard:
– Number of active restrictions is more or less equal to the number of design variables
– Sensitivity analysis become very expensive
– Solution time of optimization algorithm becomes of the same order of magnitude as the FE computation.
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Strategies to solve large scale problems
Improve the sensitivity analysis:
– Selection of potentially active constraints
– Adjoin vs direct sensitivity analysis
Introduction ‘dummy’ compliance constraint’ to control the convergence during first steps (Bruggi & Duysinx, 2013)
Use integrated stress constraints instead of a purely local approach
– Lose of local control of stress constraints: results looks closer to compliance design (Duysinx & Sigmund, 1998)
– Rather difficult to tackle with classical approximation (function not convex)
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Sensitivity analysis
Direct approach: solve n (#dv) load cases
Adjoin method: solve m (#constraints) load cases
– For one load case: m=#FE ~ n
– For several load cases: m=#FE *#load cases >n
1 0 0
0
1 1 1
2 2 T
s sK W V U
s s U V U
1
i i i
U F KK U
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Problem formulation: compliance constraint
Minimum volume with (fatigue stress) constraints and compliance constraint
Compliance constraints is introduced to provide a better stability and effectiveness to the convergence (Bruggi & Duysinx, 2012)
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Integrated (aggregated) stress constraint
Use aggregate restriction of relaxed stress constraints (Duysinx &
Sigmund, 1998)
– q-norm
– q-mean
Ordering relationship
1/*
1
( )1max 0, 1
eqNe
pe e eT
ee
1/*
1
( )1 1max 0, 1
eqNe
pe e eN T
ee
1/ 1/
* * *
1...1 1
1max
q qN N
q q q
e e ee N
e eN
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NUMERICAL APPLICATIONS: 3-BAR TRUSS
Minimum compliance design
Compliance (1,2,3) = 73.3 Nm
Max von Mises:
1) 229 N/m²
2) 571 N/m²
3) 555 N/m²
Volume = 25%
Stress constrained design
Compliance
1) 91.2 Nm
2) 45.6 Nm
3) 45.0 Nm
Max Von Mises (1,2,3)= 150N/m²
Volume = 26.4 %
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NUMERICAL APPLICATIONS: 3-BAR TRUSS
q-norm of stresses (q=4):
Bound: 500 N/m²
Compliance: 87.3, 59.3, 67.9 Nm
Max von Mises (local) for load case 1,2, 3 :
230, 235, 231 N/m²
Volume = 24.8%
q-mean of stresses (q=4):
Bound: 92 N/m²
Compliance: 90.6, 50.3, 53.8 Nm
Max von Mises (local) for load case 1,2, 3:
237, 215, 207 N/m²
Volume = 22.4%
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Large scale optimization algorithms
Fleury (2006) pointed out that the computation time of solution algorithm growths dramatically with the number of active constraints
For dual maximization algorithms the explanation is rather easy. Let’s consider the problem:
Dual function
min 1/ 2
. .
T
T
x x
s t C x d
max 1/ 2 ( )
. . 0
T T TC C d
s t
dim x = n
dim C = nxm
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Large scale optimization algorithms
Dual function maximization
Solution algorithms
Iterative Newton scheme
requires solving in various ways
max ( ) 1/ 2 ( )
. . 0
T T TC C d
s t
2
( )
( )
T
T
d C x
C C
( )( 1) 1 ( )( ) ( )kk T T kC C d C a
1( )TC C dim CTC = (mxm)
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Large scale optimization algorithms
Results based on numerical experiments by Fleury (2006) show that:
– Computation time growths more or less linearly with the number n of design variables;
– Computation time growths more or less like the power 3 of the number of active constraints.
There is an urgent need for new solvers able to tackle huge problems with simultaneously a large number of design variables and a high number of active constraints
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CONCLUSIONS & PERSPECTIVES
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CONCLUSIONS
Additive manufacturing have put forward a revived interest for solving efficiently topology optimization problems with local constraints (e.g. stress constraints)
Specific character of stress constraints
– For several load cases
– For unequal stress limits in tension and compression
– Geometrical constraint
– Several materials
Extension of stress constraints to important problems for engineering applications:
– Various failure criteria like unequal stress criteria
– Fatigue
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PERSPECTIVES
PENDING TOPICS:
Efficient treatment of large scale optimization problems including stress constraints
– Novel class of solution algorithms
Accurate calculation of the stress constraints in the framework of material distribution problems:
– Jagged / unclear boundaries
– Stress intensity factors to take into account notches, etc.
– Consider stress history i(t) instead of a single load case:
other criteria like Matake, Dang Van, Finley…
– Consider cumulative damage Palmer Milgren
Manufacturing constraints in order to generate designs which can be fabricated using AM
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THANK YOU FOR YOUR ATTENTION
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PROBLEM FORMULATION
Homogenized failure criteria predicting failure in the microstructure from macroscopic point of view:
With consistency conditions requirements: p=q
43 Rank 2 layered material SIMP (isotropic) material
*| ( ) || /| eq eq p
l
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e-relaxation: interpretation
Relaxation of stress constraints
by
Solve a sequence of perturbated problems with a decreasing sequence of e going to zero
44
0 ( ) 1
|
min ( )
. . | ( ) || (1 )
²
x
eq
l
V x dx
s t
e e
e
| ( ) ||| (1 )eq
l
e e
2
|| ( ) ||1
eq
l
ee
e
| ( ) ||| 0eq
l if
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NUMERICAL APPLICATIONS: 4-BAR TRUSS
E=100 N/m², =0.3, F =1 N, L =1 m
Von Mises
T=C=6 N/m²
Ishai
T=24 & C=6 N/m²
Ishai
T=6 & C=24 N/m²
From Swan and Kosaka (1997)
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MULTI AXIAL FATIGUE CRITERIA: CROSSLAND
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MULTI AXIAL FATIGUE CRITERIA: SINES
Assuming a SIMP model, after Finite Element discretization, one can calculate the stresses at appropriate positions (e.g. the element centroïd) using the tension matrix Te
0
First and second invariants can be computed by introducing the hydrostatic stress matrix He
0 and the von Mises quadratic stress matrix Me
0:
It is easy to recover the value of the alternate and mean stress components
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MULTI AXIAL FATIGUE CRITERIA: SINES
For topology optimization, as suggested by Duysinx & Bendsoe (1998), one should consider the micro stresses after applying the polarization factor
Sines criterion for topology optimization writes
The final expression Sines criterion for topology optimization reads
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SENSITIVITY ANALYSIS
Sensitivity analysis of fatigue stress criteria requires the sensitivity analysis of the alternate, mean, and max components.
Deriving the expression of the criteria, it comes
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SENSITIVITY ANALYSIS
Selecting the adjoin methods since we have less active stress constraints that the number of design variables, one has:
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Sensitivity analysis
Discretized equilibrium
Sensitivity of displacement vector
Direct approach: solve for every design variables
Stress constraint
K U F
1
i i i
U F KK U
TU
1
2* * * *
23 1 3 1 3T T
h D VMJ w Wq and J U VU
2 0pV V0pW W
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Sensitivity analysis
Sensitivity of unequal stress constraints: Ishai
Derivative of criteria
Adjoin approach (for every constraint)
* 0 01 1|| || /
2 2
eq eq p T
ISH ISH
s sW U U V U
s s
0 0
0
|| || 1 1 1
2 2
Teq
ISH
Ti i
s s UW V q
s s U V U
1 0 0
0
1 1 1
2 2 T
s sK W V U
s s q V q
|| ||eqTISH
i i i
g KU
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