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Computational Methods for Multiaxial Fatigue 1
Structures and Multiaxial Fatigue Analysis
Timothy LanglaisUniversity of [email protected]
Advisers: J. H. Vogel and T. R. Chasehttp://www.menet.umn.edu/˜langlais/
Computational Methods for Multiaxial Fatigue 2
Outline
1. undergraduate work on SAE Mini-Baja
2. graduate work on multiaxial fatigue
(a) project outline
(b) strain-based approach to multiaxial fatigue
(c) overview of contributions to process
(d) building an empirical plasticity model
Computational Methods for Multiaxial Fatigue 3
SAE Mini-Baja Competition
9-month project to design and build an off-road vehicle with thefollowing constraints:
❖ unmodified Briggs & Stratton Engine
❖ rollcage safety requirements
❖ $1500 cost limit
Project culminates with competition that includes
❖ acceleration
❖ braking
❖ durability
❖ flotation
Computational Methods for Multiaxial Fatigue 4
Mini-Baja Design
Observation: nearly all Mini-Baja designs use a tubular skeletondesign fitted with caulked/riveted sheet aluminum skin forflotation
❖ skin adds approximately 30 lbs. of extra weight
Idea: build main hull using a structural skin—aluminumhoneycomb panel
Computational Methods for Multiaxial Fatigue 5
Mini-Baja Testing
?How does one connect the panels?
P
❖ create a baseline 90o specimen foreach connection design
❖ test in static 3-pt bending
❖ measure failure load
Computational Methods for Multiaxial Fatigue 6
Mini-Baja Testing
Test several designs:
❖ cut inside panel sheet, fold outside panel sheet
❖ rivet aluminum doublers to the panels
❖ bond aluminum doublers to the panels
Final Design: bond and rivet alu-minum doublers to the panels
Computational Methods for Multiaxial Fatigue 7
Graduate Work on Multiaxial Fatigue
Goal: design and create a validated multiaxial fatigue analysis tool
❖ program funded by Deere & Co.
❖ application to isotropic steels used in axles, rods, etc.
❖ focus on variable-amplitude service histories with manythousands of samples
Computational Methods for Multiaxial Fatigue 8
Why Is Fatigue Important?
Fact: more than 80% of all failures in the ground vehicle industryare fatigue-related
Thus: industry must understand and be able to predict fatigue inorder to design for product life cycle
Computational Methods for Multiaxial Fatigue 9
Why Computational Multiaxial Fatigue Methods?
1. Computation is much cheaper/faster than experimentation.
❖ But answers are only as good as the underlying models.
2. Most components are subjected to multiple loads, leading to amultiaxial σ-ε state (e.g., tractor axle in bending and torsion).
❖ Can only be partially accounted for using equivalentuniaxial methods.
3. Many components are subjected to multiple loads with varyingphase.
❖ Cannot be accounted for using uniaxial or equivalentmethods.
Computational Methods for Multiaxial Fatigue 10
The Computational Approach to Fatigue
notch correction
cycle counting damage model
material properties
stressconcentrations
material properties
summation
+
plasticity
Loads, P (t)
Strains, ε(t)σ
ε
ε
εγ
σ(t
),ε(
t)
t
∑ni=0 f(Ni)
Ci(
σ,ε
),i=
0...n
Ni, i = 0...n
Nf
Computational Methods for Multiaxial Fatigue 11
Project Contributions
1. infinite-surface plasticity model
2. combined notch correction and plasticity models
3. multiaxial cycle counting algorithm
4. robust numerical implementation of damage models
5. experiments on multiaxial behavior under constrained plasticity
6. empirical plasticity modeling
Computational Methods for Multiaxial Fatigue 12
Infinite-Surface Plasticity Model
s
suαactive
Model based on the work of Mrozand Chu
❖ each surface represents a uniquevalue of the plastic modulus, H
❖ model captures material mem-ory behavior
❖ geometric implementation re-duces system to single tensordifferential equation
❖ model inaccurate for repeatednonproportional cycling
Computational Methods for Multiaxial Fatigue 13
Combining Notch Correction and Plasticity
eε
σ
eεp eεe
Notch Problem: Given nominalstrains, e, find notch σ and ε.
Kottgen’s Hypothesis: The gov-erning equations of plasticity canbe used as a structural modelto relate elastically-calculatedstrains (eε = Kte) to nonlinearnotch stresses (σ).
❖ It is possible to simultaneously solve Kottgen’s structuralmodel and the material model
Computational Methods for Multiaxial Fatigue 14
Multiaxial Cycle Counting
Sample Number
strainstress
❖ uniaxial methods assume that allchannels are in-phase
➠ only need to identify reversals onone channel
❖ uniaxial rainflow methods can onlycount cycles on peaks and valleys
➠ intermediate samples must be re-moved
❖ uniaxial methods fail to identify im-portant peaks and valleys on otherchannels
Computational Methods for Multiaxial Fatigue 15
Numerical Implementation of Damage Models
Usual numerical implementation establishes an explicit relationbetween the damage parameter and the life:
P =σ′f
E(2Nf )b + ε′f (2Nf )c
❖ requires re-fit of material properties σ′f , b, ε′f , and c for each
damage parameter
❖ assumes a relationship between the ε−Nf and σ − ε materialproperties
Computational Methods for Multiaxial Fatigue 16
Numerical Implementation of Damage Models
Instead, establish implicit relation
P = f(Nf ; σ′
f , b, ε′f , c)
❖ requires only one fit of the material properties—the uniaxialε−Nf properties will do
❖ robust: assumes nothing about how ε−Nf and σ − ε materialproperties were fit
Computational Methods for Multiaxial Fatigue 17
Multiaxial Experiments
❖ collect ε-gage data in area of con-strained plasticity near hole
❖ measure load input, P
❖ attempt to predict ε response us-ing P input
Computational Methods for Multiaxial Fatigue 18
Outline—Empirical Plasticity Model
Goal describe the process for building an empirical plasticitymodel
1. Plasticity Models
2. Building an Empirical Plasticity Model
3. Preliminary Results
Computational Methods for Multiaxial Fatigue 19
What Is a Plasticity Model?
A plasticity model is used to compute nonlinear stresses frommeasured strains via a set of governing differential equations
σ = f (ε, a, σ, H)
a = µβ
σ2y = (σ − a) : (σ − a)
σ
√3τ
a
σ
σy
❖ von Mises yield criterion:
a− center
σy− radius
❖ kinematic hardening: the yieldsurface may move but cannotgrow during loading
Computational Methods for Multiaxial Fatigue 20
What Defines a Plasticity Model
σ
a
a
σn
❖ direction of yield surface mo-tion
β =a
‖ a ‖❖ magnitude of yield surface
motion
H = f (‖ a ‖)or
µ =‖ a ‖
Note β and H or µ are both free parameters
Computational Methods for Multiaxial Fatigue 21
Experiments Behind Multiaxial Plasticity Modeling
P
T σ,ετ ,γ
❖ cannot measure yield surfacemotion (β and H or µ) di-rectly
❖ thin-walled tube experiments
❖ can measure ε =(ε, γ/
√3)
using strain gages
❖ can measure σ =(σ,√
3τ)
from loads
Computational Methods for Multiaxial Fatigue 22
Conventional Method for Building
a Plasticity Model
1. propose functions for β and H or µ based on theory orexperimental observations
2. program a plasticity model based on those functions
3. compare plasticity model’s predicted stresses against measuredstresses for strain-controlled histories
Computational Methods for Multiaxial Fatigue 23
Determination of Yield Surface Motion
from Experimental Data
1. use curve fits to find derivatives
2. Hooke’s Law:εp = ε− εe
3. Normality:
n =εp
‖ εp ‖4. Kinematic Hardening:
a = σ − σyn
H =σ : n
εp : n
β =a
‖ a ‖
Computational Methods for Multiaxial Fatigue 24
Building an Empirical Model
Find: functions or state variables that correlate theexperimentally-derived values of H or µ and β
❖ tensor that correlates the direction, β
β = f(?)
❖ scalar variable/function that correlates the magnitude, H or µ
H = f(?)
µ = f(?)
Computational Methods for Multiaxial Fatigue 25
Correlating Direction of Yield Surface Motion
-1
-0.5
0
0.5
1
-1 -0.5 0 0.5 1
Axial Backstress Rate, βa
Axi
alSt
ress
Rat
e,σ
-1
-0.5
0
0.5
1
-1 -0.5 0 0.5 1
Torsional Backstress Rate, βtTor
sion
alSt
ress
Rat
e,√ 3τ
Conclusion: Yield surface center moves in the direction of thestress rate, β ∝ σ
Computational Methods for Multiaxial Fatigue 26
Correlating Magnitude of Motion
Mroz Active Surface
σ
σact
σ
√3 τ
❖ H is a function of thesize of the largest load-ing surface in contactwith stress point, σact
10000
100000
1e+06
100 150 200 250 300 350 400 450 500 550
Plas
tic M
odul
us, H
Mroz Active Surface
uniaxialproportional
nonproportional
Computational Methods for Multiaxial Fatigue 27
Correlating Magnitude of Motion
Dafalias-Popov 2-Surface Distance
βin
βδ
σ
σ
√3 τ
❖ H is a nonlinear func-tion of β
δand β
in
10000
100000
1e+06
0 2 4 6 8 10 12 14
Plas
tic M
odul
us, H
Dafalias-Popov 2 Surface
uniaxialproportional
nonproportional
Computational Methods for Multiaxial Fatigue 28
Correlating Magnitude of Motion
Bannantine 2-Surface Distance
D
σ
σ
√3 τ
❖ H is a function of thedistance to the limitsurface, D
10000
100000
1e+06
400 600 800 1000 1200
Plas
tic M
odul
us, H
Bannantine 2 Surface
uniaxialproportional
nonproportional
Computational Methods for Multiaxial Fatigue 29
Correlating Magnitude of Motion
McDowell/Dafalias-Popov Accumulated Plastic Strain
σ
σ
√3 τ
❖ H is a function ofthe accumulated plas-tic strain,
∫ ‖ εp ‖ dt
10000
100000
1e+06
0 0.002 0.004 0.006 0.008 0.01
Plas
tic M
odul
us, H
McDowell/Dafalias-Popov Accumulated Plastic Strain
uniaxialproportional
nonproportional
Computational Methods for Multiaxial Fatigue 30
Conclusions
❖ computational analysis is an inexpensive way to evaluatefatigue
❖ it is possible to determine plasticity model parameters usingthin-walled tube data
❖ the direction of the yield surface motion roughly follows themotion of the stress point, β = a
‖a‖ ≈ σ
❖ the magnitude of the yield surface motion, H, is best correlatedby the accumulated plastic strain