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LesT It is not possible to model 10 elements across the thickness of thin plate elements in FEA. Only 1 element is formulated, used and possible. You could be referring to solid elements which do not apply to this thread. In reference to your other question about FEA being practical, if all the...

I think Daniel is asking you to mesh your entire part with linear hexahedral elements (mapped meshing). I agree with him if your part is not complex and this can be done.

okeng If a part is used in several assemblies and you only have a problem with the hole location in one bracket, then get a new part number for that one bracket. Then u do not have to revise 100 other assemblies and worry about inventory.

I have had cylindrical contact problems that did not converge, but when I tried the surface dependency it did converge. But spherical surfaces could be different than cylindrical sufaces, I have not tried that. Is there an initial gap between the two srfaces?

Have u tried the surface dependency feature? This will ensure the same mesh on both contact surfaces and element normals will meet.

check your boundary conditions. You might have rigid body movements.

Acording to the criterion often applied to define a thin plate (for purposes of technical calculations) the ratio of the thickness to the smaller span length should be less than 1/20. fsi

Try a 90 degrees arc support instead of point support. fsi

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proe2003 Just to clarify somethings here: plasticity is material nonlinearity where as stress sitffening and large displacement are geometric nonlinearities. fsi

proe2003 If Ansys is set up like IDEAS, then your first point should be (0.00095,26100) not (0.0,0.0), If you delete (0.0, 0.0) , I think you should get the correct results. fsi

I agree u should get the same results if your stresses and strains are in the elastic range. Check your setting for nonlinear model and check your load factor, time, etc. There is some setting that is kicking you into nonlinearity before it is time. Having said that strain of .001 and stress of...

what is the yield point of material? Your first point on the stress strain curve data should be the yield point. If this is how u input data and your yield point is about 13000 psi then your results make sense, otherwise check ur stress strain data points. fsi

UG NX2 and UG NX2.0.1 maintenance have already been released. fsi

If you are using NX2 , there was a maintenance released on 11/6/03. You might want to try that and see if that will correct your problem. fsi

put ur cursor on the grid line . Double arrow cursor comes on. Drag the grid line to where you want. Let it go. fsi

Yes it makes it harder. For steels, the relationship between the minimum ultimate tensile strength and the Brinell hardness number is found to be Su=0.45Hb kpsi from Mechanical Engineering Design by Shigley fsi

if you have large deflections, you have a situation called bending with stress stiffening. what happens the plate starts carrying membrane stresses even though load is normal to it. outer perimeter will be in tangential compression due to strss stiffening. your actual deflection will be less...

It is not that simple. see if you can find the following articles. K. p. Singh "An approximate analysis of fondation stresses in horizontal pressure vessels" ASME PUBLICATION PAPER NO. 79-NE-1, 1979 call Holtec International 609.797.0900 ask them to send you a copy of this paper...

change your IDEAS memory setting to manual. In windows change ur total paging file size for virtual memory to 2000 mb. Then it gets additional memory from hard disk . In IDEAS change ur total virtual memory limit to about 800-900 mb. fsi