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Ansys contact Ansys contact Ansys contact Ansys contact Ansys contact
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Ansys Contact usages: tips and tricks Let us talk about convergence ANSYS, Inc. Proprietary © 2004 ANSYS, Inc.
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Page 1: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

Let us talk about convergence

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Page 2: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

One reason for convergence difficulties could be the following:Suggestion

• FE Model is not modeled correctly in a physical sense1) If you use a point load to do a plastic analysis, you will never get the converged solution.

Because of the singularity at the node, on which the concentrated force is applied, the stress is infinite. The local singularity can destroy the whole system convergence behavior. The same thing holds for the contact analysis. If you simplify the geometry or use a too coarse mesh (with the consequence that the contact region is just a point contacta too coarse mesh (with the consequence that the contact region is just a point contact instead of an area contact) you most likely will end up with some problems in convergence.

point load σ Geometry Mesh

εε

l ti l i t t l i

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plastic analysis contact analysis

Page 3: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:• FE Model is not modeled correctly in a numerical sense

2) A possible rigid body motion is quite often the reason which causes divergence in a contact analysis This could be the result of the following: We always believe that if we

g g

contact analysis. This could be the result of the following: We always believe, that if we model the gap size as zero from geometry, it should also be zero in the FE model. But due to the mathematical approximation and discretization, it does not have necessarily to be zero anymore. Exactly, this can kill the convergence. If possible, use KEYOPT(5) to close

the gap. You can also use KEYOPT(9)=1 to ignore 1% penetration, if it is modeled.

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

KEYOPT(5)=1KEYOPT(5)=0

Page 4: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:• Numerically bad conditioned FE Model

4) ANSYS uses the penalty method as a basis to solve the contact problem and the convergence behavior largely depends on the penalty stiffness itself. A semi-default value

g g

convergence behavior largely depends on the penalty stiffness itself. A semi default valuefor the penalty stiffness is used, which usually works fine for a bulky model, but might not be suitable for a bending dominated problem or a sliding problem. A sign for bad conditioning is that the convergence curve runs parallel to the the convergence norm. Choosing a smaller

l f FKN l k th bl i t If th l i i tvalue for FKN always makes the problem easier to converge. If the analysis is not converging, because of the too much penetration, turn off the Lagrange multiplier.The result is usually not as bad as you would believe.

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

FKN=1 FKN=0.01

Page 5: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

Suggestion

One reason for convergence difficulties could be the following:• Numerically bad conditioned FE Model

One reason for convergence difficulties could be the following:

FKN=.1 FKN=0.0001

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FKN=0.0001FKN=.1

Page 6: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

• Load step is too large  Error in element formulation or element is turned inside out 5) If it is a large deflection problem, you usually need more substeps. 5 to 10 substeps are

good if the rotations are not too large (<180 degrees) If it is a small deflection problem you

g g

good if the rotations are not too large (<180 degrees). If it is a small deflection problem, you should reduce FKN, because FKN*d produces a large force, which can destroy the element.

NLGEO,ONNSUB,1,1,1 NLGEO,ON

S

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

NSUB,10,100,1

Page 7: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

• Quads instead of triads Error in element formulation or element is turned inside out 6) If some elements are locally distorted you might get an error in the element formulation or

the element is even turned inside out Try to use a coarser mesh in this region to avoid

g g

the element is even turned inside out. Try to use a coarser mesh in this region to avoid those problems. You can also use NCNV,0 to continue the analysis and ignore those local problems if they do not effect the global equilibrium. In general, try to use triangular, tetrahedral or hexahedral elements (linear). Do not use quadratic hexahedral elements.

Error in element formulation

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Linear quads Mid-side triads

Page 8: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

• The parts have no unique minimum potential energy position.7) If the max. DOF increment is not getting smaller and the force convergence norm keeps

almost constant probably some parts in the model are oscillating Here introducing a small

g g

almost constant, probably some parts in the model are oscillating. Here, introducing a small friction coefficient is usually better than using a weak spring, not knowing exactly where to place it. Friction can be applied to all contact elements (try MU=0.01 or 0.1)

MU=0.1MU=0

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Page 9: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

• Unreasonable defined contact pair8) Sometimes it is also important to think about possible contact configurations: Which surface

or point will be in contact with which surface ??? The way to define the contact or target canor point will be in contact with which surface ??? The way to define the contact or target can influence the convergence behavior as shown below.

Target

Contact

g

Contact

Target

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Page 10: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

• Unreasonable defined plastic material11) It is not always a good idea to define the tangential stiffness to be zero using a plastic

material law If the yield stress is reached all over the whole cross section there is no

g g

material law. If the yield stress is reached all over the whole cross section, there is no material resistance anymore to carry the load. There will be a plastic hinge and so the solution will never converge. In this case, input the correct tangential stiffness.

Plastic strain Stress strain curve with

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

tangential slope zero

Page 11: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

• Unreasonable defined plastic material

g g

Plastic strainPlastic strainStress strain curve with tangential slope 10000

Contact region

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Stress distribution

Page 12: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:• Instable solution

13) Some time, the solution could be instable, if the static analysis type is used, e.g if the contact region changes abruptly In this case you can use more load steps strategy to get

One reason for convergence difficulties could be the following:

contact region changes abruptly. In this case, you can use more load steps strategy to get rid of the instable solution.

Instable point Next solutionFE model

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Instable point Next solutionFE model

Page 13: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionOne reason for convergence difficulties could be the following:

TIP• Instable solution TIP

Load step-1 ends shortly Load step-2 starts shortlyFE model

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Load step 1, ends shortly before the snap through

Load step 2, starts shortly after the snap through.

FE model

Page 14: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

Suggestion/prep7et,1,182,2et 2 169

lsel,s,,,5nsll,s,1

/solunlgeom on

TIPet,2,169et,3,171,,1,,1mp,ex,1,2e5mp,mu,1,.1mp,prxy,1,.3

type,2esurflsel,s,,,2,3nsll,s,1type,3

nlgeom,onnsub,100,100,1outres,all,allnsel,s,loc,y,0d,all,alll l 6 1

In order to model the contact region r,1,,,.001,,,-2r,2,,,.001,,,-2rect,0,1,0,3wpof,1,3wprot,-20

type,3esurflsel,s,,,2nsll,s,1type,2real 2

lsel,s,,,6,,,1d,all,uxd,all,uy,-.5allssolv

greasonably, you should define two contact pairs, one for load step-1 and another for load step-2, and use the node detection option(KEYOPT(4)=1 as shown below p ,

rect,-.2,3,0,.2esize,.2amesh,1esize,.1ames all

real,2esurflsel,s,,,5,8,3nsll,s,1type,3

/COM Load step-2lsel,s,,,6,,,1d,all,uxd,all,uy,-1alls

option(KEYOPT(4)=1, as shown below.

ames,all esurfallsnsub,10,10,1solv

Status-1

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Contact-1 Target-1Target-2 Contact-2

Status-2

Page 15: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

SuggestionGood mesh will generally make problem easier to converge.• The fine mesh and similar are always good the contact simulation:

GeometryGeometry Contact regionContact region

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Contact meshContact mesh

Page 16: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

How can I make the problem converge?• Trust yourself: I’m able to make it converge!Trust yourself: I m able to make it converge!• Consider the problem as idealized real world problem:

20% M h i ti 20% E i ti20%- Mechanics expertise, 20%- Engineer expertise 30%- FEA expertise, 30%- Software expertise

• Use the magic KEYOPTIONS

KEYOPT(5) 1 T li i t th i id b d tiKEYOPT(5)=1: To eliminate the rigid body motion

KEYOPT(9)=1: To eliminate the geometric noiseKEYOPT(9)=1: To eliminate the geometric noise

KEYOPT(10)=2: To make ANSYS think

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

( )

Page 17: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

Table of Contents

1. Introduction2. MPC connection for SOLID-SOLID, SHELL-SHELL ,3. MPC connection for SOLID-SHELL4. MPC connection SOLID-BEAM and SHELL-BEAM5. MPC connection between the FE model and loading point

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Page 18: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

1. Introduction, What is MPC?

• MPC means: Multipoint Constraint PC )( ijCCL

≠+∑• MPC means: Multipoint Constraint PC

)1()( )3()1( LROTZSinUY •=+4

)(01

ijCuCu jj

ji ≠=+∑=

)2()1()2()(

)1()()3()2(

)()(

LROTZSinUYLROTZSinUY

+•=−

•=+

L

L

31

LL2

Beam

)(20)2()1(

)3()2()1( ROTZSinLUYUY •−−=

+

MPC

LL

SolidMPC

For small rotation:)(20 )3()2()1( ROTZLUYUY •−−=

)1(UY )3(ROTZ

LROTZUYUYCE 2,,3,1,,2,1,,1,0,2, −−

)(20 ROTZLUYUY

)2(UY

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Page 19: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

1. Introduction, What do you need MPC?

• To connect the dissimilar mesh:– If the geometries are not topologically connected, you can mesh the geometry

independently and connect the FE model via MPC.

Geometry Dissimilar meshConnected via MPC

Stress distribution

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Connected via MPC

Page 20: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

• To connect the different element types:

1. Introduction, What do you need MPC? y

– If the different element types are used on the connection region, because of the different DOFs, the connectivity is not consistent. The consistence can be achieved in the FE model via MPC.

Geometry Solids and Shells Connected via MPC

Deformation

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

Connected via MPC

Page 21: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

• To apply the remote load:

1. Introduction, What do you need MPC?

pp y– If the loading point is not connected to the FE model, the connection can be

achieved in the FE model via MPC.

Loading point and FE model Connected via MPC

Stress distributions

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Page 22: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

1. Introduction, Why the existing contact algorithm is not used?

• The results may depend on specified contact stiffness• The results may depend on specified contact stiffness.– The existing bonded contact algorithm using the penalty method, because of

contact stiffness(cause the ill-conditioning) and the penetration, it might influence the accuracy of the resultinfluence the accuracy of the result.

• Multiple iterations are required to adjust penetration in order to satisfy equilibrium even for small deformation problemssatisfy equilibrium even for small deformation problems.

– This will cause the iteration, even for linear problem.

• Occasionally spurious natural frequencies can occur in modal analysis• Occasionally spurious natural frequencies can occur in modal analysis.– This is because of the contact stiffness used.

Only translational DOFs are treated• Only translational DOFs are treated.– This will cause the accuracy problem, if the distance between the contact and

target is not zero.Sh ll/b bl t b h dl d

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– Shell/beam assembly can not be handled.

Page 23: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

1. Introduction, Why the existing contact algorithm is not used?

It i l it bl f ll t i• It is only suitable for small strain.– Because the existing CE method always uses the original nodal orientation.

• The RBE3 constraint can only support low order elements. – 10 nodes tetrahedron element are most commonly used element.

• It is not allowed to apply displacement constraints on the master node of RBE3

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Page 24: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

1. Introduction, Advantages of new MPC approach

• Build MPC equations internallyBuild MPC equations internally.– It is not necessary to define the equations by hand, the user treats the

connection as bonded contact, ANSYS will generate automatically the MPC.

• Degrees of freedom of the contact surface nodes are eliminated.– This will improve solution efficiency.

• No contact stiffness is required as an input.– The accuracy of the solution is not dependent on try-and-error anymore.

F ll d f i bl i “ li ”• For small deformation problem, it represents “true linear contact” behavior.

– No iteration is needed in solving system equations.

• For large deformation problems, the MPC equations are updated during each iteration.

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Page 25: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

1. Introduction, Advantages of new MPC approach

N t l t l ti l b t t ti l d f f d l b• Not only translational but rotational degrees of freedom can also be constrained.

– It will improve the solution accuracy, and makes the connection between solid-shell shell shell solid beam and shell beam more reasonableshell, shell-shell, solid-beam and shell-beam more reasonable.

• The generation of internal MPC is also very easy thanks to contact i d fi i ipair definition.– For the users, it is nothing new, if you know how to define the contact.

• It is not like MSC/Nastran (RBE3 type)

– Shape functions are taken into account automatically; no weight factor p y; gis needed.

– not only forces but also displacements can be applied.

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Page 26: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

2. MPC connection for SOLID-SOLID, SHELL-SHELL

Model-1: mesh is pretty Model-2: mesh is quite Model-2: consistent

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similar SMAX=1.71 q

different SMAX=1.71 mesh SMAX=1.71

Page 27: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

2. MPC connection for SOLID-SOLID, SHELL-SHELL

KEYOPT(9)=0 KEYOPT(9)=1

If you have the geometry penetration:1) Set the PINBALL to catch the contact2) Use KEYOPT(9)=1 to ignore the

Model-2: Penetration and KEYOPT(9)=1 SMAX=1.71

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) ( ) gpentration

Page 28: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

2. MPC connection for SOLID-SOLID, SHELL-SHELL

KEYOPT(9)=0 KEYOPT(9)=1

If you have the geometry gap:1) Set the PINBALL to catch the contact2) Use KEYOPT(9)=1 to ignore the

Model-2: Gap and KEYOPT(9)=1 SMAX=1.73

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

2) Use KEYOPT(9)=1 to ignore the pentration

Page 29: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

2. MPC connection for SOLID-SOLID, SHELL-SHELL MPC connection for SHELL-SHELL(Edge-to-Edge)( g g )

Contact175

Target170Target170

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Page 30: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

2. MPC connection for SOLID--SHELL Summary: For most applications, default KEYOPT(5)=0 or 3 can be used. Many test cases show the best solution with KEYOPT(5)=2cases show the best solution with KEYOPT(5)=2.

New Virtual New Contact

New VirtualVirtual

shell elements

SHELL181

New Contact elements

CONTA175

Virtual

shell elements

MPC equations

shell edge – solid surface

FTOLN

Influence di t

MPC equations

(translation DOF only)

Virtual shell - solid surface

Shell thickness

MPC equations

(translation + Rotation DOF)

shell edge - virtual

FTOLN

Influence distance

gshell distance

KEYOPT(5)=1 KEYOPT(5)=2SHSD ID

KEYOPT(5)=0,3

3rd Approach: 1st Approach: 2nd Approach:

SHSD,ID SHSD,ID

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

ppshell-solid constraintsolid-solid constraint

ppshell-shell constraint

Page 31: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

P d

3. MPC connection SOLID-BEAM and SHELL-BEAM

Procedure:1) Treat the solid surface and/or shell edge as contact surface, treat the beam

node as target pilot node. No additional target is needed.2) S t th t t l t k ti2) Set the contact element keyoptions:

KEYOPT(2)=2 this will activate the MPC methodKEYOPT(12)=5 or 6 Set the bonded contact keyKEYOPT(4)=1 Force-distributed surfaceKEYOPT(4)=2 Rigid constraint surface

3) Run the analysis

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Page 32: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

3. MPC connection SOLID-BEAM and SHELL-BEAM/prep7et,1,45

vext,all,,,,,150acle,all

et,2,188et,3,173,,2 !KEYOPT(2)=2Keyopt,3,4,1 !KEYOPT(4)=1keyopt,3,12,5 !KEYOPT(12)=5

acle,allk,100,0,0,150k,101,0,0,300k,102,1,1,150l,100,101

et,4,170mp,ex,1,2e5mp,prxy,1,0.3SECTYPE, 1,BEAM, CTUBE

l,100,101lsel,s,,,33LATT,1,,2,,102,,1 lmes,33real,10

SECOFFSET, CENT SECDATA,10,11 pcir,10,11,0,90pcir,10,11,90,180

real,10type,4tshap,pilo !Pilot node on beame,2017 !Pilot node on beamnsel,s,loc,z,150 SOLID-BEAM

pcir,10,11,180,270pcir,10,11,270,360numm,kplesi,4,,,2

i 8

nsel,s,loc,z,150nsel,u,,,2017esel,s,type,,1type,3Esurf !Contact on solid

esiz,,8et,10,42esha,2type,10

ll

Esurf !Contact on solid/solunsel,s,loc,z,0d,all,allnsel,s,loc,z,300

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

ames,allesiz,,20type,1

, , , ,f,2018,fx,1000alls

Page 33: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

3. MPC connection SOLID-BEAM and SHELL-BEAMExample

Solid solution Solid-Beam via MPC

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Page 34: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

3. MPC connection SOLID-BEAM and SHELL-BEAM/prep7et,1,181

adra,1,4,7,10,,,6real 2et,1,181

et,2,188et,3,175,,2,,2 !KEYOPT(2)=2Keyopt,3,4,2 !KEYOPT(2)=2keyopt,3,12,5 !KEYOPT(12)=5

real,2ames,5,8k,100,0,0,150k,101,0,0,300k 102 1 1 150keyopt,3,12,5 !KEYOPT(12) 5

et,4,170mp,ex,1,2e5mp,prxy,1,0.3r,2,1

k,102,1,1,150l,100,101lsel,s,,,18LATT,1,,2,,102,,2 lmes 18r,2,1

SECTYPE, 2, BEAM, CTUBE SECOFFSET, CENT SECDATA,10,11pcir,0,10.5,0,90

lmes,18real,10type,4tshap,piloe,673 SHELL-BEAMpcir,0,10.5,0,90

pcir,0,10.5,90,180pcir,0,10.5,180,270pcir,0,10.5,270,360numm,kp

e,673nsel,s,loc,z,150nsel,u,,,673esel,s,type,,1type,3numm,kp

lsel,s,,,1,10,3lesi,all,,,8esha,2esiz,,20

type,3esurf/solunsel,s,loc,z,0d,all,all

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

es ,, 0k,50k,51,0,0,150l,50,51

d,all,allnsel,s,loc,z,300f,674,fx,1000alls

Page 35: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

P d

4. MPC connection between the FE model and loading point

Procedure:1) Treat the FE surface and/or edge as contact surface, treat the loading node

as target pilot node. No additional target is needed.2) S t th t t l t k ti2) Set the contact element keyoptions:

KEYOPT(2)=2 this will activate the MPC methodKEYOPT(12)=5 or 6 Set the bonded contact keyKEYOPT(4)=1 Force-distributed surfaceKEYOPT(4)=2 Rigid constraint surface

3) Run the analysis

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Page 36: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

4. MPC connection between the FE model and loading point/prep7 et,1,42et,1,42et,2,169et,3,171,,2,,11 !KEYOPT(2)=2 !KEYOPT(4)=1keyopt,3,12,5 !KEYOPT(12)=5mp,ex,1,2e5p,e , , e5mp,prxy,1,.3 rect,0,10,0,2esiz,1ames,1,n,100,5,5lsel,s,,,2nsll,s,1type,3yp ,real,3esurfallstype,2yp ,tshape,pilote,100nsel,s,loc,x,0d,all,all

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

, ,allsf,100,fy,-100

Page 37: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

4. MPC connection between the FE model and loading point

KEYOPT(4) 1KEYOPT(4)=1Force-distributed surface

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KEYOPT(4)=2Rigid constraint surface

Page 38: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

4. MPC connection between the FE model and loading point

KEYOPT(4)=1Force-distributed surface

KEYOPT(4)=2Rigid constraint surface/prep7

et,1,42n,1000,0,0lsel,s,,,5,8, ,

et,2,169et,3,171,,2,,1keyopt,3,12,5 mp,ex,1,2e5

, ,,, ,nsll,s,1type,3real,3esurf

/solunsel,s,loc,x,-10d,all,all

llp, , ,mp,prxy,1,.3 rect,-10,10,-5,5pcir,3asba,1,2

allstype,2tshape,pilote,1000

allsf,1000,mz,-.7e6nlgeo,onsolv

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

, ,smrt,4ames,all

,

Page 39: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

4. MPC connection between the FE model and loading point

Bending moment Torsion momentShear forceBending moment Torsion momentShear force

/prep7 cylin,10,20,0,100,0,90 type,3 /soluet,1,45et,2,170et,3,173,,2,,1keyopt,3,12,5

1 2

*rep,4,,,,,90,90numm,kpesiz,3vmes,all

10000 0 0 100

real,3esurfallstype,2

h il

nsel,s,loc,zd,all,allallsf,10000,mx,4.766e3

ll

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

mp,ex,1,2e5mp,prxy,1,.3

n,10000,0,0,100asel,s,,,2,20,6nsla,s,1

tshape,pilote,10000

allssolv

Page 40: Ansys contact Ansys contact Ansys contact

Ansys Contact usages: tips and tricks

4. MPC connection between the FE model and loading point

Bending moment Torsion momentShear forceg Torsion moment

/prep7 et,1,63et 2 170

cylin,10,20,0,100esiz,3

type,3real,3

/solunsel,s,loc,z

et,2,170et,3,175,,2,,1r,1,1keyopt,3,12,5 mp ex 1 2e5

ames,3,4n,10000,0,0,100lsel,s,,,9,12nsll,s,1

esurfallstype,2tshape,pilot

d,all,allallsf,10000,mx,4.766e3

ANSYS, Inc. Proprietary© 2004 ANSYS, Inc.

mp,ex,1,2e5mp,prxy,1,.3

e,10000 allssolv


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