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Center for Computer Aided Design
Automotive Research Centerarc
CAD-BASED DESIGN PROCESS FORFATIGUE ANALYSIS, RELIABILITY-
ANALYSIS, AND DESIGN OPTIMIZATION
CAD-BASED DESIGN PROCESS FORFATIGUE ANALYSIS, RELIABILITY-
ANALYSIS, AND DESIGN OPTIMIZATION
K.K. Choi, V. Ogarevic, J. Tang, and Y.H. ParkCenter for Computer-Aided Design
College of EngineeringThe University of Iowa
Iowa City, IA 52242
Center for Computer Aided Design
Automotive Research Centerarc
CONTENTS OF THE PROCESS
l Create a Pro/E CAD Model of a Typical Passenger VehicleSystem and Automatically Translate It Into DADSDynamics Model
l Perform Dynamics Simulation of the Car Model Over aTypical Road Profile
l Create Parameterized CAD Model and FE Models of theFront Right Lower Control Arm
l Perform Fatigue Life Analysis of the Lower Control Arm
l Perform CAD-Based Fatigue Design Sensitivity Analysisand Optimization of the Lower Control Arm
l Reliability-Based Analysis and Design Optimization
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Pro/E MODEL OF THE VEHICLE SYSTEM
26 Bodies Model
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DADS MODEL OF THE VEHICLE SYSTEM
l Total of 22 Rigid Bodies
l Simulation Parameters:n 7 seconds straight line run
n RMS2 road profile: 0.316in. average peak to valleyheight
n Speed 10 m/sec
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FRONT RIGHT SUSPENSION
X
FR_Lower Control Arm
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Pro/E MODEL OF THE LOWERCONTROL ARM
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JOINT REACTION FORCE HISTORIES(X-Direction at Three Joints)
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FE MODEL OF THE LOWERCONTROL ARM
l Total Number of Elements: 297
l Element Type: ANSYS 20-Node Solid
l Total Number of Nodes: 1977
l Total Number of DoF: 5931
l Mesh Generator: MSC/PATRAN
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FATIGUE LIFE PREDICTIONAPPROACH
l Obtain and Convert Joint Reaction Forces and InertialForces From Rigid or Flexible Multibody DynamicsSimulation in the Format Readable by DRAW
l Create FE Models That Are Consistent with the CADModel of the Structural Component
l Superimpose Stress Time Histories for All Surface Nodesof the FE Model Using Hybrid Method
l Perform Preliminary Analysis To Identify Critical Regions
l Perform Refined Analysis for Higher Fidelity Fatigue LifePredictions
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COMPUTATIONAL FLOW CHART
Pro/EFEA ToolANSYS &NASTRAN
DynamicAnalysisDADS
CADModel(LCA)
GeometryPATRAN orHyperMesh
FE Model
FrameInformation
DADSOutput File
InterfaceDADS_READER
DynamicInformation
Load VectorCalculation Tool
DynamicParameters
Quasi StaticLoad Vectors
StressCoefficients
SuperpositionTool
Dynamic StressTime History
PreliminaryAnalysis Tool
RefinedAnalysis Tool
CriticalRegion
Crack Initiation Life
VehicleSystem
DRAW
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STRESS HISTORY AT CRITICAL NODE(Three Principal Stresses)
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ALGORITHM FOR FATIGUE LIFEPREDICTIONS IN DRAW
l Compute Stress/strain and Damage Parameter History
l Edit and Rainflow Count Damage Parameter History
l Identify Surface Critical Region Using PreliminaryLife Analysis with von Mises Strain Approach
l Estimate Elastic-plastic Strain at Critical Region
l Refine Life Predictions at Critical Region Using vonMises Strain Approach or More Advanced CriticalPlane Approaches
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ESTIMATION OF ELASTIC-PLASTICSTRAINS
l Uniaxial Case:n Neuber’s Rule and Remberg-Osgood Equation
l Multiaxial Case:n Equivalent strain energy density approach
n Assumed elastic-plastic loading paths
n Currently linear kinematic hardening plasticity model(Mroz Model) is being implemented
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LIFE PREDICTION METHODS
l Equivalent Strain Methods:n Von Mises equivalent strain approach with Smith-
Watson-Topper theory
n ASME Boiler and Pressure Vessel Code approach
l Critical Plane Methods:n Tensile strain based critical plane approach
(Fatemi-Socie)
n Shear strain based critical plane approach(Fatemi-Kurath)
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FATIGUE CRACK INITIATION LIFECONTOUR
(Preliminary Analysis with von Mises Equivalent-Strain Approach)
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CRITICAL REGION IDENTIFICATIONPROCEDURE
l User Selected Points
l Preliminary FatigueAnalysisn Calculate linear elastic von
Mises strain
n Calculate fatigue crackinitiation life for all surfacenodes
n Select critical nodes withminimum life
n The procedure is automatedin DRAW
LIST OF CRITICAL NODES
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REFINED FATIGUE ANALYSIS AT THECRITICAL NODES(Equivalent Strain Method)
NodeNo.
560
583
590
PreliminaryAnalysis
Cycles Years
Refined Analysis(with Neuber)
Cycles Years
Refined Analysis(with EP)
Cycles Years
2.8901E8
3.2312E8
1.217E10
2.8295E8
3.1671E8
2.7053E8
2.2432E8
3.5239E8
3.9165E8
64 62 50
78
87
70
60
72
2700
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CAD-BASED SHAPE OPTIMIZATIONAPPROACH
l Implement CAD-based Shape Design ParameterizationCapability within Pro/E Environment
l Use HyperMesh or PATRAN for Mesh Generation,ANSYS or NASTRAN for FEA, and DRAW for FatigueLife Prediction
l Develop a Design Velocity Field Computation MethodBased on Pro/E Shape Design Parameter
l Hybrid Method Is Used for Sensitivity Computationn Continuum DSA for Sensitivity of the Dynamic Stresses
n Finite Difference for Sensitivity of the Fatigue Life
l DOT Is Used for CAD-based Shape Design Optimization
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COMPUTATIONAL FLOW CHART
Pro/ENGINEER
DesignParameterization
Velocity FiledComputation
Pro/EEnvironment
Mesh GeneratorHyperMesh or PATRAN
DRAW
DSA
DOT
DesignUpdate
DesignOptimization
Trade-offDetermination
What-ifStudy
SensitivityDisplay
CADModeler
DesignParameterization
Velocity FieldComputation
Mesh Generator
Life Prediction
DSO
4-StepDesign Process
DesignOptimization
SensitivityAnalysis
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CAD-BASED DESIGN PARAMETERIZATION
l CAD Model Must BeWell-Constructed :• Able to regenerate
perturbed models inlarge design space
• Maintain topologywhen regenerating
• Exported geometrymust support meshgeneration byHyperMesh orPATRAN
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DESIGN PARAMETERIZATION
l Design Parameters Are Chosen From Pro/E FeatureDimensions Such as Length, Radii, General Surface, etc.
l Design Parameters Selection by Pointing and Clicking atPro/E Display
l Identify FE Nodes on CAD Surfacesn PATRAN generates a file including FE surface node information
n This step is automated if meshes are generated by Pro/E
l Boundary Design Velocity Fields Are Computed UsingFinite Difference Method Based on CAD Regeneration
l Domain Velocity Fields (Velocity of Interior Nodes) AreComputed Using Boundary Displacement Method
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SELECTED DESIGN PARAMETERS
s1
s2
s3
s4
s5 s6
d1043d1044d1036d1037d1029d1030d837d838d842d843d854d855
height at s1width at s1height at s2width at s2height at s3width at s3height at s4width at s4height at s5width at s5height at s6width at s6
Design Parameter Description
l Independent Section Dimensions (Heights and Widths) Are Selectedas Design Parameters
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OPTIMIZATION PROBLEM
l Objective Function - Minimize Volume
l 66 Constraint Functions - Fatigue LifeLonger Than 11 Years at 66 CriticalNodes
l 12 Shape Design Parameters
l MFD Algorithm Is Used forOptimization
DP Value(mm) Lower Bd Upper Bd
d1043d1044d1036d1037d1029d1030
d837d838d842d843d854d855
12.07.015.07.024.09.0
22.017.026.018.034.019.0
DP Value(mm) Lower Bd Upper Bd
25.025.519.010.019.09.0
35.035.529.020.029.019.0
17.012.020.013.029.014.0
30.030.524.015.024.014.0
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DESIGN HISTORY
l Optimal Design Is Obtained in 11 Iterations
Cost Function History Design Parameter History
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LIFE CONTOUR AT INITIAL ANDOPTIMAL DESIGNS
Initial Design Optimal Design
Volume(mm ) Initial Optimal3
195786.5 173787.8
DP Initial (mm) Optimal
d1043d1044d1036d1037d1029d1030
d837d838d842d843d854d855
DP Initial (mm) Optimal
17.012.020.013.029.014.0
30.030.524.015.024.014.0
17.39.826.07.031.110.9
25.025.519.013.120.79.0
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DESIGN OPTIMIZATION STARTING FROMTWO DIFFERENT INITIAL DESIGNS
Initial Design I Initial Design II
Volume(mm ) Design I Design II3
195786.5 210118.1
DP Design I Design II
d1043
d1044
d1036
d1037
d1029
d1030
d837
d838
d842
d843
d854
d855
DP Design I Design II
17.0
12.0
20.0
13.0
29.0
14.0
30.0
30.5
24.0
15.0
24.0
14.0
17.0
16.0
20.0
17.0
29.0
18.0
30.0
30.5
24.0
15.0
24.0
14.0
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COMPARISON OF OPTIMAL DESIGNS OFINITIAL DESIGNS I & II
Optimal Design I Optimal Design II
Volume(mm ) Design I Design II3
173787.8 173809.0
DP Design I Design II
d1043
d1044
d1036
d1037
d1029
d1030
d837
d838
d842
d843
d854
d855
DP Design I Design II
17.3
9.8
26.0
7.0
31.1
10.9
25.0
25.5
19.0
13.1
20.7
9.0
17.4
9.8
26.0
7.0
31.3
10.6
25.0
25.5
19.0
12.7
20.6
9.0
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RELIABILITY-BASED DESIGNOPTIMIZATION (RBDO)
l Mathematical Formulation:
Distributional and deterministic designvectors θ=[θ1,θ2,...,θn1]T and b=[b1,b2,...,bn2]
min. W(b,θθ)
s.t.
l Reliability Constraints Are Assumed to beMutually Independent and No CorrelationExists Between Them
Pf i= P(g i(b,θ) ≤ 0) ≤ Pf i
U , i = 1− m
b jL ≤ b j ≤ b j
U , j =1 − n1
θkL ≤ θk ≤ θk
U , k = 1 − n2
Design ModelDefinition
FORM forFailure Functions
Optimum?
Reliability-BasedDSA
UpdateDesignModel
STOPYes
No
OptimizationAlgorithms
(DOT)
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RANDOM VARIABLE SPACESl Transformation Matrix T: U = T(X) from a non-normally distributed
random variable space X to a standard normally distributed randomvariable space U where
U i = Φ −1( fXi(x)), i = 1− n
U2
U1
X2
0
0
Pf
β
Failure Regiong(U) < 0
MPP U*
Major Contributionto Failure ProbabilityFrom this Area
(FORM)
Failure Surfaceg(X) = 0 Failure Surface
g(U) = 0
MPP U*
Mean ValuePoint
f (x)X
(SORM)
Cumulative DistributionFunction (CDF)
Φ:
b
X1
Safe Regiong(U) > 0
0
f (u)U
ReliabilityIndex β
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NUMERICAL EXAMPLETRACKED VEHICLE ROAD ARM
Roadarm
101
11
12
13
14
15
16
17
X
X
3
2
4
5
6
7
8
9
X
RR
RR
RR
RR
R
R
RR
RR
R
R
12
3
l Multibody Dynamics Model: 17 Rigid Bodies
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SHAPE DESIGN PARAMETERIZATION
Intersection 1Intersection 2
Intersection 3
Intersection 4
20 in.
1x'
3x'
2x'
2x'
1x'
Design Parameters:b1, b3, b5, b7 Design Parameters:
b2, b4, b6, b8
Cross Sectional Shape
StraightLines
Cubic Curves
3x'
bi, i = 1,3,5,7
bi, i = 2,4,6,8
1236
12TorsionBar
Center of theRoadwheel
1x'
3x'
2x'
Intersection 1b1, b2 Intersection 2
b3, b4 Intersection 3b5, b6
Intersection 4b7, b8
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DETERMINISTIC DESIGN OPTIMIZATION
l Objective Function - Minimize Volume
l Constraint Function - 24 Fatigue Life Greater Than20 Years
1x'3
x'
2x'1x'
3x'
2x'
12271287
1544
1340
11401023
843505547
439
1391
12161311
14331519
926
9221012
1008
918
742
472
1380 1129
Function Description Lower Bound Current Design StatusCost Volume 487.678 in3
Constraint 1 Life at node 1216 9.63E+6 (20 Year) 9.631E+6 blocks ActiveConstraint 2 Life at node 926 9.63E+6 (20 Year) 8.309E+7 blocks InactiveConstraint 3 Life at node 1544 9.63E+6 (20 Year) 8.926E+7 blocks InactiveConstraint 4 Life at node 1519 9.63E+6 (20 Year) 1.447E+8 blocks InactiveConstraint 5 Life at node 1433 9.63E+6 (20 Year) 2.762E+8 blocks Inactive
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RANDOM VARIABLES FORRELIABILITY ANALYSIS
Random Variables Mean Value Standard Deviation Distribution
Young’s Modulus E 30.0E+6 0.75E+6 LogNormal
Fatigue Strength Coefficient s'f 1.77E+5 0.885E+4 LogNormal
Fatigue Ductility Coefficient e'f 0.41 0.0205 LogNormal
Fatigue Strength Exponent b -0.07300 0.00365 Normal
Fatigue Ductility Exponent c -0.6 0.003 Normal
Tolerance b1 2.889 in. 0.032450 Normal
Tolerance b2 1.583 in. 0.019675 Normal
Tolerance b3 2.911 in. 0.031703 Normal
Tolerance b4 1.637 in. 0.019675 Normal
Tolerance b5 2.870 in. 0.031703 Normal
Tolerance b6 2.420 in. 0.026352 Normal
Tolerance b7 2.801 in. 0.032496 Normal
Tolerance b8 4.700 in. 0.050568 Normal
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FOUR-STEP INTERACTIVE DESIGNl Reliability-Based Design Model Definition
n Objective function - minimize volume
n Constraints - failure probability of fatigue life Š 1%
n Design parameters - mean values of b1 to b8
l Interactive Designn An improved design obtained in two iterations
n 10 FORMs, 2 Reliability-Based DSAs (5 days on HP9000/755)
Function Description Pf = F(-b) Pf = F(-b) Changes
at “Optimum” 2 RB Designs
Cost Volume 436.722 in3 447.691 in3 2.5%
Constraint 1 Life at node 1216 0.476% 0.532% 0.056
Constraint 2 Life at node 926 3.24% 0.992% -2.2
Constraint 3 Life at node 1544 3.21% 0.998% -2.2
Constraint 4 Life at node 1519 0.83% 0.721% -0.11
Constraint 5 Life at node 1433 0.023% 0.018% -0.005
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SUMMARY AND CONCLUSIONSl The Connection Between Pro/E and DADS Seems to Be Working
Properly and Efficiently
l DRAW Code Efficiently Identified Fatigue Critical Regions During thePreliminary Analysis
l DRAW Refined Analysis Provided Higher Fidelity Predictions on theFatigue Critical Locations
l DSO Provided Accurate Design Sensitivity Information Very Efficiently
l Very Similar Optimal Designs Are Obtained from Two Different InitialDesigns
l CAD-Based Design Model Is Critical for Multidisciplinary CAE Analysisand Design Optimization
l CAD-Based Design Model Will Allow Connection of CAE to CAD-CAM
l Reliability-Based Design Optimization Provides High Quality DesignsThat Are Cost Effective in Manufacturing Process