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Everything posted by Mrt

  1. you can try to use radioss quasi-static. to my mind radioss is better for contact ussues;)
  2. do you want connect "node to node"? or "node to node set"?
  3. are you kidding?=) @Ekaterina needs more topics!
  4. The penalization technique used is the “power law representation of elasticity properties,” which can be expressed for any solid 3D or 2D element as follows: K(r) = K*ρ^p where K and K represent the penalized and the real stiffness matrix of an element, respectively, ρ is the density and p the penalization factor which is always greater than 1. In OptiStruct, the DISCRETE parameter corresponds to (p - 1). DISCRETE can be defined on the DOPTPRM bulk data entry. P usually takes a value between 2.0 and 4.0. For example, compared to the non-penalized formulation (which is equivalent to p=1) at ρ=0.3, p=2 reduces the stiffness of the element from 0.3 to 0.09 times the stiffness of the fully dense element. The default DISCRETE is 1.0 for shell dominant structures, and 2.0 for solids dominant structures (the dominance is defined by the proportion of number of elements)
  5. i haven't done mesh fo cfd, i haven't ever worked in acusolve. as for me the best way to try=) do cube, and do diffrent approach/mesh size.=)
  6. https://altairuniversity.com/wp-content/uploads/2015/11/Optim_Interpretation.pdf
  7. you can't use one size fo all model. as i know you should use min/max and grow rate parameters. and my question to @acuprowhy can't i use several volumes separated by wall?
  8. hello! i am not cfd specialist. you do great job! it's interesting issue. is it windshield defrost? you should make 2 volumes. first are tubes second is cabin. and the WALL should be common part for tube and cabin (mesh node to node).
  9. what solver do you use? in optistruct is possible to do tie contact automatic=) tools->contact brouser->entities field mouse right button->autocontact->property type "freeze" for tie
  10. try to solve reduced model/part of model. it's difficult to search mistake in large model.
  11. have you tried to solve part of model? Has it gone? maybe it's so large for your computer?
  12. clear all previous files in work folder (close hyperview if it is opened). check penetration.
  13. it's interesting phenomena=) looks like scale factor 6 on OY=)
  14. hello, @Roy Duan! what tool did you use? have you ever used this feature for midmesh? Direct Midmesh Quick Start Guide - v1.pdf
  15. =) i think so if @Prakash Pagadala say that it wasn't possible you can't do it.
  16. did you solve eigenfrequency? in frequency/modal analysis displacement/stress doesn't matter. could your explain what did you do? and show, please, your result pics.
  17. optistruct reference guide=) opti control->
  18. could you show result pics and load pics? you have more grids in your model now and it can change your loading.
  19. @LOKESH KATARI DOFs are depended on element numbers/types. quad shell first order has 4 points and 6 dofs on every point=24 DOFs. If you create full vehicle model which contains 100.000 points (only shell elements and beams) you will have 6*100.000 DOFs if you separete chassis from full model and it will include only 50.000 points you can estimate your reduction coefficient=)
  20. try "-nt 2" or delete options -both and check "use SMP:-nt 2"
  21. at first-Do you use HyperMesh? or LSprepost? your surface: just mesh it!=) like this, Anna! p.s. i don't know why, but in this area your mesh shoulbe like in my pic below... otherwise HM won't make solid mesh right. if your solver will be dyna you should know about timestep.=)
  22. your mesh is good, guy! don't worry=) just unchek "min size"
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