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Transcript of FEM Stress Concepts
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FEAConcepts:SWSimulationOverview J.E.Akin
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3 ConceptsofStressAnalysis3.1 Introduction
Heretheconceptsofstressanalysiswillbestatedinafiniteelementcontext.Thatmeansthattheprimary
unknownwillbethe(generalized)displacements.Allotheritemsofinterestwillmainlydependonthe
gradientofthedisplacementsandthereforewillbelessaccuratethanthedisplacements.Stressanalysis
coversseveralcommonspecialcasestobementionedlater.Hereonlytwoformulationswillbeconsidered
initially.Theyarethesolidcontinuumformandtheshellform.BothareofferedinSWSimulation.Theydiffer
inthatthecontinuumformutilizesonlydisplacementvectors,whiletheshellformutilizesdisplacement
vectorsandinfinitesimalrotationvectorsattheelementnodes.
AsillustratedinFigure31,thesolidelementshavethreetranslationaldegreesoffreedom(DOF)asnodal
unknowns,foratotalof12or30DOF.Theshellelementshavethreetranslationaldegreesoffreedomaswell
asthreerotationaldegreesoffreedom,foratotalof18or36DOF.ThedifferenceinDOFtypesmeansthatmomentsorcouplescanonlybeapplieddirectlytoshellmodels.Solidelementsrequirethatcouplesbe
indirectlyappliedbyspecifyingapairofequivalentpressuredistributions,oranequivalentpairofequaland
oppositeforcesattwonodesonthebody.
Shellnode Solidnode
Figure31Nodaldegreesoffreedomforframesandshells;solidsandtrusses
Stresstransfertakesplacewithin,andon,theboundariesofasolidbody.Thedisplacementvector,u,atany
pointinthecontinuumbodyhastheunitsofmeters[m],anditscomponentsaretheprimaryunknowns.The
componentsofdisplacementareusuallycalledu,v,andwinthex,y,andzdirections,respectively.Therefore,
theyimplytheexistenceofeachother,u(u,v,w).Allthedisplacementcomponentsvaryoverspace.Asin
theheattransfercase(coveredlater),thegradientsofthosecomponentsareneededbutonlyasan
intermediatequantity.Thedisplacementgradientshavetheunitsof[m/m],orareconsidereddimensionless.
Unliketheheattransfercasewherethegradientisuseddirectly,instressanalysisthemultiplecomponentsof
thedisplacementgradientsarecombinedintoalternateformscalledstrains.ThestrainshavegeometricalinterpretationsthataresummarizedinFigure32for1Dand2Dgeometry.
In1D,thenormalstrainisjusttheratioofthechangeinlengthovertheoriginallength,x=u/x.In2Dand
3D,bothnormalstrainsandshearstrainsexist.Thenormalstrainsinvolveonlythepartofthegradientterms
paralleltothedisplacementcomponent.In2Dtheyarex=u/xandy=v/y.AsseeninFigure32(b),
theywouldcauseachangeinvolume,butnotachangeinshapeoftherectangulardifferentialelement.A
shearstraincausesachangeinshape.Thetotalanglechange(from90degrees)isusedastheengineering
definitionoftheshearstrain.Theshearstrainsinvolveacombinationofthecomponentsofthegradientthat
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areperpendiculartothedisplacementcomponent.In2D,theengineeringshearstrainis=(u/y+v/x),asseeninFigure32(c).Strainhasonecomponentin1D,threecomponentsin2D,andsixcomponentsin
3D.The2Dstrainsarecommonlywrittenasacolumnvectorinfiniteelementanalysis,=(xy)T.
Figure32Geometryofnormalstrain(a)1D,(b)2D,and(c)2Dshearstrain
Stressisameasureoftheforceperunitareaactingonaplanepassingthroughthepointofinterestinabody.
Theabovegeometricaldata(thestrains)willbemultipliedbymaterialpropertiestodefineanewphysical
quantity,thestress,whichisdirectlyproportionaltothestrains.ThisisknownasHookesLaw:=E,(see
Figure33)wherethesquarematerialmatrix,E,containstheelasticmodulus,andPoissonsratioofthe
material.The2Dstressesarewrittenasacorrespondingcolumnvector,=(xy)T.Unlessstatedotherwise,theapplicationsillustratedhereareassumetobeinthelinearrangeofamaterialproperty.
The2Dand3DstresscomponentsareshowninFigure34.Thenormalandshearstressesrepresentthe
normalforceperunitareaandthetangentialforcesperunitarea,respectively.Theyhavetheunitsof
[N/m^2],or[Pa],butareusuallygivenin[MPa].Thegeneralizationsoftheengineeringstraindefinitionsare
seeninFigure35.Thestrainenergy(orpotentialenergy)storedinthedifferentialmaterialelementishalf
thescalarproductofthestressesandthestrains.Errorestimatesfromstressstudiesarebasedonprimarily
onthestrainenergy(orstrainenergydensity).
Figure33Hooke'sLawforlinearstressstrain,=E
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Figure34Stresscomponentsin2D(left)and3D
Figure35Graphicalrepresentationsof3Dnormalstrains(a)andshearstrains
3.2 Axialbarexample
Thesimplestavailablestressexampleisanaxialbar,showninFigure36,restrainedatoneendandsubjected
toanaxialload,P,attheotherendandtheweightisneglected.Letthelengthandareaofthebarbedenoted
byL,andA,respectively.ItsmaterialhasanelasticmodulusofE.Theaxialdisplacement,u(x),varieslinearly
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fromzeroatthesupporttoamaximumofattheloadpoint.Thatis,u(x)=x/L,sotheaxialstrainisx=u
/x=/L,whichisaconstant.Likewise,theaxialstressiseverywhereconstant,=E=E/Lwhichinthe
casesimplyreducesto=P/A.Likemanyothermorecomplicatedproblems,thestressheredoesnot
dependonthematerialproperties,butthedisplacementalwaysdoes, .Youshouldalwayscarefullycheckboththedeflectionsandstresseswhenvalidatingafiniteelementsolution.
Sincetheassumeddisplacementislinearhere,anyfiniteelementmodelwouldgiveexactdeflectionandthe
constantstressresults.However,iftheloadhadbeenthedistributedbarweighttheexactdisplacement
wouldbequadraticinxandthestresswouldbelinearinx.Then,aquadraticelementmeshwouldgiveexact
stressesanddisplacementseverywhere,butalinearelementmeshwouldnot.
Theelasticbarisoftenmodeledasalinearspring.Inintroductorymechanicsofmaterialstheaxialstiffnessof
abarisdefinedask=EA/L,wherethebarhasalengthofL,anareaA,andisconstructedofamaterialelastic
modulusofE.Thentheabovebardisplacementcanbewrittenas ,likealinearspring.
=P/A,=PL/EA
Figure36Alinearlyelasticbarwithanaxialload
3.3 StructuralmechanicsModernstructuralanalysisreliesextensivelyonthefiniteelementmethod.Themostpopularintegral
formulation,basedonthevariationalcalculusofEuler,isthePrincipleofMinimumTotalPotentialEnergy.
Basically,itstatesthatthedisplacementfieldthatsatisfiestheessentialdisplacementboundaryconditionsand
minimizesthetotalpotentialenergyistheonethatcorrespondstothestateofstaticequilibrium.Thisimplies
thatdisplacementsareourprimaryunknowns.Theywillbeinterpolatedinspaceaswilltheirderivatives,and
thestrains.Thetotalpotentialenergy,,isthestrainenergy,U,ofthestructureminusthemechanicalwork,
W,donebytheexternalforces.Fromintroductorymechanics,themechanicalwork,W,donebyaforceisthe
scalardotproductoftheforcevector,F,andthedisplacementvector,u,atitspointofapplication.
Thewellknownlinearelasticspringwillbereviewedtoillustratetheconceptofobtainingequilibrium
equationsfromanenergyformulation.Consideralinearspring,ofstiffnessk,thathasanappliedforce,F,at
thefree(right)end,andisrestrainedfromdisplacementattheother(left)end.Thefreeendundergoesa
displacementof.Theworkdonebythesingleforceis
.Thespringstorespotentialenergyduetoitsdeformation(changeinlength).Herewecallthatstrainenergy.
Thatstoredenergyisgivenby
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Therefore,thetotalpotentialenergyfortheloadedspringis
Theequationofequilibriumisobtainedbyminimizingthistotalpotentialenergywithrespecttotheunknown
displacement,.Thatis,
Thissimplifiestothecommonsinglescalarequation
k=F,whichisthewellknownequilibriumequationforalinearspring.Thisexamplewasslightlysimplified,sincewe
startedwiththeconditionthattheleftendofthespringhadnodisplacement(anessentialorDirichlet
boundarycondition).Nextwewillconsideraspringwhereeitherendcanbefixedorfreetomove.Thiswill
requirethatyoubothminimizethetotalpotentialenergyandimposethegivendisplacementrestraint.
Figure37Theclassicandgenerallinearspringelement
Nowthespringmodelhastwoenddisplacements,1and2,andtwoassociatedaxialforces,F1andF2.The
netdeformationofthebaris=21.Denotethetotalvectorofdisplacementcomponentsas
andtheassociatedvectorofforcesas
Thenthemechanicalworkdoneonthespringis
1F1+2F2Thenthespring'sstrainenergyis
,
wherethespringstiffnessmatrixisfoundtobe
.Thetotalpotentialenergy,,becomes
.
Notethateachtermhastheunitsofenergy,i.e.forcetimeslength.Thematrixequationsofequilibriumcome
fromsatisfyingthedisplacementrestraintandtheminimizationofthetotalpotentialenergywithrespectto
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eachandeverydisplacementcomponent.Theminimizationrequiresthatthepartialderivativeofallthe
displacementsvanish:
,or
.
Thatrepresentsthefirststagesystemofalgebraicequationsofequilibriumfortheelasticsystem:
.Thesetwosymmetricequationsdonotyetreflectthepresenceofanyessentialboundaryconditiononthe
displacements.Therefore,nouniquesolutionexistsforthetwodisplacementsduetoappliedforces(theaxial
RBMhasnotbeeneliminated).Mathematically,thisisclearbecausethesquarematrixhasazerodeterminate
andcannotbeinverted.Ifallofthedisplacementsareknown,youcanfindtheappliedforces.Forexample,if
youhadarigidbodytranslationof1=2=CwhereCisanarbitraryconstantyouclearlygetF1=F2=0.Ifyou
stretchthespringbytwoequalandoppositedisplacements;1=C,2=Candthefirstrowofthematrix
equationsgivesF1=2kC.ThesecondrowgivesF2=2kC,whichisequalandoppositetoF1,asexpected.
Usually,youknowsomeofthedisplacementsandsomeoftheforces.Thenyouhavetomanipulatethematrix
equilibriumsystemtoputitintheformofastandardlinearalgebraicsystemwhereaknownsquarematrix
multipliedbyavectorofunknownsisequaltoaknownvector: .3.4 Equilibriumofrestrainedsystems
Liketheoriginalspringproblem,nowassumetherightforce,F2,isknown,andtheleftdisplacement,,hasagiven(restrained)value,say.Then,theabovematrixequationrepresentstwouniqueequilibriumequationsfortwounknowns,thedisplacement2andthereactionforce.Thatmakesthislinearalgebraicsystemlookstrangebecausethereareunknownsonbothsidesoftheequals,=.Youcould(butusuallydo
not)correctthatbyrearrangingtheequationsystem(notdoneinpractice).First,multiplythefirstcolumnof
thestiffnessmatrixbytheknownvalueandmoveittotherightside:
andthenmovetheunknownreaction,,totheleftside
.
Nowyouhavetheusualformofalinearsystemofequationswheretherightsideisaknownvectorandthe
leftsideistheproductofaknownsquarematrixtimesavectorofunknowns.Sinceboththeenergy
minimizationandthedisplacementrestraintshavebeencombinedyounowhaveauniquesetofequationsfor
theunknowndisplacementsandtheunknownrestraintreactions.Invertingthe2by2matrixgivestheexact
solution:
sothatF1F2always,asexpected.If=0,asoriginallystated,thentheenddisplacementis .Thissortofrearrangementofthematrixtermsisnotdoneinpracticebecauseitdestroysthesymmetryofthe
originalequations.Algorithmsfornumericallysolvingsuchsystemsrelyonsymmetrytoreduceboththe
requiredstoragesizeandtheoperationscount.Theyareveryimportantwhensolvingthousandsofequations.
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3.5 Generalequilibriummatrixpartitions
Theabovesmallexamplegivesinsighttothemostgeneralformofthealgebraicsystemresultingfromonly
minimizingthetotalpotentialenergy:asingularmatrixsystemwithmoreunknownsthanequations.Thatis
becausethereisnotauniqueequilibriumsolutiontotheproblemuntilyoualsoapplytheessential(Dirichlet)
boundaryconditionsonthedisplacements.Thealgebraicsystemcanbewritteninageneralpartitionedmatrix
formthat
more
clearly
defines
what
must
be
done
toreduce
the
system
toasolvable
form
by
utilizing
essentialboundaryconditions.
Foranelasticsystemofanysize,thefull,symmetricmatrixequationsobtainedbyminimizingtheenergycan
alwaysberearrangedintothefollowingpartitionedmatrixform:
whereurepresentstheunknownnodaldisplacements,andgrepresentsthegivenessentialboundaryvalues(restraints,orfixtures)oftheotherdisplacements.ThestiffnesssubmatricesKuuandKggaresquare,whereasKugandKguarerectangular.InafiniteelementformulationallofthecoefficientsintheKmatricesareknown.TheresultantappliednodalloadsareinsubvectorFgandtheFutermsrepresenttheunknowngeneralized
reactionsforcesassociatedwithessentialboundaryconditions.ThismeansthataftertheenforcementoftheessentialboundaryconditionstheactualremainingunknownsareuandFu.Onlythendoesthenetnumberofunknownscorrespondtothenumberofequations.But,theymustberearrangedbeforealltheremaining
unknownscanbecomputed.
Here,forsimplicity,ithasbeenassumedthattheequationshavebeennumberedinamannerthatplacesrows
associatedwiththegivendisplacements(essentialboundaryconditions)attheendofthesystemequations.
Theabovematrixrelationscanberewrittenastwosetsofmatrixidentities:
.
Thefirstidentitycanbesolvedfortheunknowndisplacements,,byputtingitinthestandardlinearequationformbymovingtheknownproducttotherightside.Mostbooksonnumericalanalysisassumethatyouhavereducedthesystemtothissmaller,nonsingularform()beforetryingtosolvethesystem.Invertingthesmallernonsingularsquarematrixyieldstheuniqueequilibriumdisplacementfield:
.Theremainingreactionforcescanthenberecovered,ifdesired,fromthesecondmatrixidentity:
.Inmostapplications,thesereactiondatahavephysicalmeaningsthatareimportantintheirownright,or
usefulinvalidatingthesolution.However,thispartofthecalculationisoptional.
3.6 StructuralComponentFailure
Structuralcomponentscanbedeterminedtofailbyvariousmodesdeterminedbybuckling,deflection,natural
frequency,strain,orstress.Strainorstressfailurecriteriaaredifferentdependingonwhethertheyare
consideredasbrittleorductilematerials.Thedifferencebetweenbrittleandductilematerialbehaviorsis
determinedbytheirresponsetoauniaxialstressstraintest,asinFigure38.Youneedtoknowwhatclassof
materialisbeingused.SWSimulation,andmostfiniteelementsystems,defaulttoassumingaductilematerial
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anddisplaythedistortionalenergyfailuretheorywhichisusuallycalledtheVonMisesstress,oreffective
stress,eventhoughitisactuallyascalar.Abrittlematerialrequirestheuseofahigherfactorofsafety.
Figure38Axialstressstrainexperimentalresults
3.7 FactorofSafety
Allaspectsofadesignhavesomedegreeofuncertainty,asdoeshowthedesignwillactuallybeutilized.For
allthereasonscitedabove,youmustalwaysemployaFactorofSafety(FOS).Somedesignersrefertoitasthe
factorofignorance.RememberthataFOSofunitymeansthatfailureiseminent;itdoesnotmeanthatapart
orassemblyissafe.Inpracticeyoushouldtrytojustify1
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6 GeometryofMesh Defeaturingcanintroduceerrors.Elementsizesandlocation
areimportant.Lookinglikethepartisnotenough.
7 Loading Areloadspreciseordotheycomefromwaveaction,etc.
8 Materialdata Isthematerialwellknown,orvalidatedbytests
9 Reliability Mustthereliabilityofthedesignbehigh
10 Restraints Designsaregreatlyinfluencedbyassumedsupports
11 Stresses Wasstressconcentrationconsidered,orshockloads
3.8 ElementTypeSelection
Evenwithtodaysadvancesincomputingpoweryouseemnevertohaveenoughcomputationalresourcesto
solvealltheproblemsthatpresentthemselves.Frequentlysolidelementsarenotthebestchoicefor
computationalefficiency.Theanalystsshouldlearnwhenotherelementtypescanbevalidorwhentheycan
beutilizedtovalidateastudycarriedoutwithadifferentelementtype.SWSimulationoffersasmallelement
librarythatincludesbars,trusses,beams,frames,thinplatesandshells,thickplatesandshells,andsolid
elements.Therearealsospecialconnectorelementscalledrigidlinksormultipointconstraints.
Theshellsandsolidelementsareconsideredtobecontinuumelements.Theplateelementsareaspecialcase
offlatshellswithnoinitialcurvature.Solidelementformulationsincludethestressesinalldirections.Shells
areamathematicalsimplificationofsolidsofspecialshape.Thinshells(likethinbeams)donotconsiderthe
stressinthedirectionperpendiculartotheshellsurface.Thickshells(likedeepbeams)doconsiderthe
stressesthroughthethicknessontheshell,inthedirectionnormaltothemiddlesurface,andaccountfor
transversesheardeformations.
LethdenotethetypicalthicknessofacomponentwhileitstypicallengthisdenotedbyL.Thethicknessto
lengthratio,h/L,givessomeguidanceastowhenaparticularelementtypeisvalidforananalysis.Whenh/Lis
largesheardeformationisatitsmaximumimportanceandyoushouldbeusingsolidelements.Conversely,
whenh/L
isvery
small
transverse
shear
deformation
isnot
important
and
thin
shell
elements
are
probably
the
mostcosteffectiveelementchoice.Intheintermediaterangeofh/Lthethickshellelementswillbemostcost
effective.Thethickshellsareextensionsofthinshellelementsthatcontainadditionalstrainenergyterms.
Theoverlappingh/LrangesforthethreecontinuumelementtypesaresuggestedinFigure39.Thethickness
ofthelinessuggeststhoseregionswhereaparticularelementtypeisgenerallyconsideredtobethepreferred
elementofchoice.Theoverlappingrangessuggestwhereonetypeofelementcalculationcanbeusedto
validateacalculatedresultobtainedwithadifferentelementtype.Validationcalculationsincludethe
differentapproachestoboundaryconditionsandloadsrequiredbydifferentelementformulations.Theyalso
canindirectlycheckthatauseractuallyunderstandshowtoutilizeafiniteelementcode.
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Draft
3.9 SWSThesymbolsu
Figure310.
T
elementsolut
representsth
areoftenrefe
displacement
enoughrestra
Al
Forsimplicit
Thatis,they
thetypeofr
frequentlye
understand
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imulationsedinSWSim
hesymbols
fo
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rredtoasgen
DOFsforthe
intstopreven
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lthreedispla
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manyfinite
enforceanI
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Displacem
Figu
tionOvervie
ght2009.All
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Fixtureaulationtorep
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tanymodelfr
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igure310Fix
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re311Singl
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ent:
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for
solids
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mbolstranslational
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heabovewor
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desareseen
garigidbody
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ctlyapplyco
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androtational
adingsare
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inFigure311.
ranslationor
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ro
ids(top)and
mpleterestr
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tenthemost
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tation
straints(fixtu
pes
DOFatanod
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in
th
ngmeansth
translations
lsfortheunk
.Youalmosta
rigidbodyrota
frameorshel
splacements
tationsarez
hellnodes
aintsatafac
orshells.Ac
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restraints.Y
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J
3
areshowngr
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.E.Akin
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ining
is.You
der
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3.10SymmetryDOFonaPlane
Aplaneofsymmetryisflatandhasmirrorimagegeometry,materialproperties,loading,andrestraints.
Symmetryrestraints\iareverycommonforsolidsandforshells.Figure312showsthatforbothsolidsand
shells,thedisplacementperpendiculartothesymmetryplaneiszero.Shellshavetheadditionalconditionthat
theinplanecomponentofitsrotationvectoriszero.Ofcourse,theflatsymmetryplaneconditionscanbe
statedinadifferent
way.
For
asolid
element
translational
displacements
parallel
tothe
symmetry
plane
are
allowed.Forashellelementrotationisallowedaboutanaxisperpendiculartothesymmetryplaneandits
translationaldisplacementsparalleltothesymmetryplanearealsoallowed.
Nodeofasolidortrusselement:
Displacementnormaltothesymmetryplaneiszero.
Nodeofaframeorshellelement:
Displacementnormaltothesymmetryplaneandtwo
rotationsparalleltoitarezero.
Figure312Symmetryrequireszeronormaldisplacement,andzeroinplanerotation
3.11AvailableLoading(Source)Options
Mostfiniteelementsystemshaveawiderangeofmechanicalloads(orsources)thatcanbeappliedtopoints,
curves,surfaces,andvolumes.ThemechanicalloadingterminologyusedinSWSimulationisinTable32.
Mostofthoseloadingoptionsareutilizedinlaterexampleapplications.
Table32Mechanicalloads(sources)thatapplytotheactivestructuralstudy
LoadType Description
BearingLoad Nonuniformbearingloadonacylindricalface
CentrifugalForce Radialcentrifugalbodyforcesfortheangularvelocityand/ortangential
bodyforcesfromtheangularaccelerationaboutanaxis
Force Resultantforce,ormoment,atavertex,curve,orsurface
Gravity Gravity,orlinearaccelerationvector,bodyforceloading
Pressure Apressurehavingnormaland/ortangentialcomponentsactingona
selectedsurface
RemoteLoad/
Mass
Allowsloadsormassesremotefromtheparttobeappliedtothepart
bytreatingtheomittedmaterialasrigid
Temperature Temperaturechangeatselectedcurves,surfaces,orbodies(see
thermalstudiesformorerealistictemperaturetransfers)
3.12AvailableMaterialInputsforStressStudies
Mostapplicationsinvolvetheuseofisotropic(directionindependent)materials.Theavailablemechanical
propertiesfortheminSWSimulationarelistedinTable33.Itisbecomingmorecommontohavedesigns
utilizinganisotropic(directiondependent)materials.Themostcommonspecialcaseofanisotropicmaterialsis
theorthotropicmaterial.Anyanisotropicmaterialhasitspropertiesinputrelativetotheprincipaldirectionsof
thematerial.Thatmeansyoumustconstructtheprincipalmaterialdirectionsreferenceplaneorcoordinate
axesbeforeenteringorthotropicdata.Mechanicalorthotropicpropertiesaresubjecttosometheoretical
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relationshipsthatphysicallypossiblematerialsmustsatisfy(suchaspositivestrainenergy).Thus,
experimentalmaterialpropertiesdatamayrequireadjustmentbeforebeingacceptedbySWSimulation.
Table33Isotropicmechanicalproperties
Symbol Label Item
E
EX
Elastic
modulus
(Youngs
modulus)
NUXY PoissonsratioG GXY Shearmodulus
DENS Massdensity SIGXT Tensilestrength(Ultimatestress) SIGXC Compressionstresslimit SIGYLD Yieldstress(yieldstrength) ALPX Coefficientofthermalexpansion
Table34Orthotropicmechanicalpropertiesinprincipalmaterialdirection
Symbol Label Item
Ex EX ElasticmodulusinmaterialXdirection
Ey EY ElasticmodulusinmaterialYdirection
Ez EZ ElasticmodulusinmaterialZdirection
xy NUXY PoissonsratioinmaterialXYdirectionsyz NUYZ PoissonsratioinmaterialYZdirectionsxz NUXZ PoissonsratioinmaterialXZdirectionsGxy GXY ShearmodulusinmaterialXYdirections
Gyz GYZ ShearmodulusinmaterialYZdirections
Gxz GXZ ShearmodulusinmaterialXZdirections
DENS Massdensity SIGXT Tensilestrength(Ultimatestress) SIGXC Compressionstresslimit SIGYLD Yieldstress(Yieldstrength) ALPX ThermalexpansioncoefficientinmaterialX ALPY ThermalexpansioncoefficientinmaterialY ALPZ ThermalexpansioncoefficientinmaterialZNote:NUXY,NUYZ,andNUXZarenotindependent
Partscanalsobemadefromorthotropicmaterials(asshownlater).However,theirutilizationismost
commoninlaminatedmaterials(laminates)wheretheyeachplylayerhasacontrollableprincipalmaterial
direction.TheconceptforconstructinglaminatesfromorthotropicmaterialplysisshowninFigure.
Understandingthefailuremodesoflaminatesusuallyrequiresspecialstudy.
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Figure313Exampleofafourplylaminatematerial
3.13StressStudyOutputs
Asuccessfulrunofastudywillcreatealargeamountofadditionaloutputresultsthatcanbedisplayedand/or
listedinthepostprocessingphase.DisplacementsaretheprimaryunknowninaSWSimulationstressstudy.
Theavailabledisplacementvectorcomponentsarecited inTable35andTable36,alongwiththereactions
theycreateifthedisplacementisusedasarestraint.Thedisplacementscanbeplottedasvectordisplays,or
contourvalues.Theycanalsobetransformedtocylindricalorsphericalcomponents.
Table35Outputresultsforsolids,shells,andtrusses
Symbol Label Item Symbol Label Item
Ux UX Displacement(Xdirection) Rx RFX Reactionforce(Xdirection)
Uy UY Displacement(Ydirection) Ry RFY: Reactionforce(Ydirection)
Uz UZ Displacement(Zdirection) Rz RFZ Reactionforce(Zdirection)
Ur URES: Resultantdisplacement
magnitude
Rr RFRES Resultantreactionforce
magnitude
Table36Additionalprimaryresultsforbeams,plates,andshellsSymbol Label Item Symbol Label Item
x RX Rotation(Xdirection) Mx RMX: Reactionmoment(Xdirection)y RY Rotation(Ydirection) My RMY Reactionmoment(Ydirection)z RZ Rotation(Zdirection) Mz RMZ: Reactionmoment(Zdirection) Mr MRESR Resultantreactionmoment
magnitude
The strains and stresses are computed from the displacements. The stress components available at an
elementcentroidoraveragedatanodearegiven inTable37. Thesixcomponents listedonthe left inthat
tablegivethegeneralstressatapoint(i.e.,anodeoranelementcentroid).Thosesixvaluesareillustratedon
theleftofFigure314.TheycanbeusedtocomputethescalarvonMisesfailurecriterion.Theycanalsobe
usedtosolveaneigenvalueproblemfortheprincipalnormalstressesandtheirdirections,whichareshownontherightofFigure314. Themaximumshearstressoccursonaplanewhosenormal is45degreesfromthe
direction of P1. The principal normal stresses can also be used to compute the scalar vonMises failure
criterion.
ThevonMiseseffectivestressiscomparedtothematerialyieldstressforductilematerials.Failureispredicted
tooccur(basedonthedistortionalenergystoredinthematerial)whenthevonMisesvaluereachestheyield
stress.Themaximumshearstressispredictedtocausefailurewhenitreacheshalftheyieldstress.SW
Simulationusestheshearstressintensitywhichisalsocomparedtotheyieldstresstodeterminefailure
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(becauseitistwicethemaximumshearstress).ThefirstfourvaluesontherightsideofTable37areoften
representedgraphicallyinmechanicsasa3DMohrscircle(seeninFigure315).
Table37:Nodalandelementstressresults
Symbol Label Item Symbol Label Item
x SX Normalstressparalleltoxaxis 1 P1 1stprincipalnormalstressy SY Normalstressparalleltoyaxis 2 P2 2ndprincipalnormalstressz SZ Normalstressparalleltozaxis 3 P3 3rdprincipalnormalstressxy TXY ShearinYdirectiononplanenormaltoxaxis
INT Stressintensity(P1P3),twicethemaximumshearstress
xz TXZ ShearinZdirectiononplanenormaltoxaxis
yz TYZ ShearinZdirectiononplanenormaltozaxis
vm VON vonMisesstress(distortionalenergyfailurecriterion)
Figure314Thestresstensor(left)anditsprincipalnormalvalues
Figure315ThethreedimensionalMohr'scircleofstressyieldtheprincipalstresses
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Ifdesired,youcanplotallthreeprincipalcomponentsatonce.Thethreeprincipalnormalstressesatanode
orelementcentercanberepresentedbyanellipsoid.Thethreeradiioftheellipsoidrepresentthemagnitudes
ofthethreeprincipalnormalstresscomponents,P1,P2,andP3.Thesignofthestresses(tensionor
compression)arerepresentedbyarrows.ThecolorcodeofthesurfaceisbasedonthevonMisesvalueatthe
point,ascalarquantity.Ifoneoftheprincipalstressesiszero,theellipsoidbecomesaplanarellipse.Ifthe
threeprincipalstresseshavethesamemagnitude,theellipsoidbecomesasphere.Inthecaseofsimple
uniaxialtensilestress,theellipsoidbecomesaline.
Figure316AprincipalstressellipsoidcoloredbyvonMisesvalue
TheavailablenodaloutputresultsinTable37areobtainedbyaveragingtheelementvaluesthatsurroundthe
node.Youcanalsoviewthemasconstantvaluesattheelementcentroids.Thatcangiveyouinsighttothe
smoothnessoftheapproximation.Forbrittlematerialsyoucanalsobeinterestedintheelementstrain
results.TheyarelistedinTable38.Table39showsthatyoucanalsoviewtheelementerrorestimate,ERR
whichisused
todirect
adaptive
solutions,
and
the
contact
pressure
from
an
iterative
contact
analysis.
Additionaloutputsareavailableifyouconductanautomatedadaptiveanalysistoreducethe(mathematical)
errortoaspecificvalue,ortorecoverresultsfromthedevelopedpressurebetweencontactingsurfaces.They
arelistedinTable39.
Table38Elementcentroidalstraincomponentresults
Sym Label Item Sym Label Item
x EPSX Normalstrainparalleltoxaxis
1 E1 Normalprincipalstrain(1stprincipaldirection)
y EPSY Normalstrainparalleltoyaxis
2 E2 Normalprincipalstrain(2ndprincipaldirection)
z EPSZ Normalstrainparalleltozaxis
3 E3 Normalprincipalstrain(3rdprincipaldirection)
xy GMXY ShearstraininYdirectiononplanenormaltoxaxis
r ESTRN Equivalentstrainxz GMXZ ShearstraininZdirectionon
planenormaltoxaxis
SED SEDENS Strainenergydensity(per
unitvolume)
yz GMYZ ShearstraininZdirectiononplanenormaltoyaxis
SE ENERGY Totalstrainenergy
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Table39Additionalelementcentroidstressrelatedresults
Label Item
ERR Elementerrormeasuredinthestrainenergynorm
CP Contractpressuredevelopedonacontactsurface