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ank

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Everything posted by ank

  1. How to find the stress singularity and how to deal with it ?
  2. Is this problem is anywhere related to contact ?
  3. If the penetration are unavoidable what to do ?
  4. WARNING ZERO OR NEGATIVE SUB-VOLUME : 3D-ELEMENT ID
  5. RUN KILLED : ENERGY ERROR LIMIT REACHED
  6. In one of my simulation ERR values goes to 99 % and then simulation stops what could be the reason for the same ?
  7. NC= 4500 T= 4.4900E-03 DT= 1.0000E-06 ERR= 0.0% DM/M= 1.1356E+00 ELAPSED TIME= 1237.04 s REMAINING TIME= 1518.03 s RESTART FILES: saddle_2_0001_[0001-0001].rst WRITTEN NC= 5000 T= 4.9900E-03 DT= 9.9999E-07 ERR= 0.1% DM/M= 1.1356E+00 ELAPSED TIME= 1379.18 s REMAINING TIME= 1384.68 s ANIMATION FILE: saddle_2A006 WRITTEN NC= 5500 T= 5.4900E-03 DT= 1.0000E-06 ERR= 0.1% DM/M= 1.1357E+00 ELAPSED TIME= 1520.82 s REMAINING TIME= 1249.32 s NC= 6000 T= 5.9900E-03 DT= 1.0000E-06 ERR= 0.1% DM/M= 1.1357E+00 ELAPSED TIME= 1666.80 s REMAINING TIME= 1115.82 s ANIMATION FILE: saddle_2A007 WRITTEN NC= 6500 T= 6.4900E-03 DT= 9.9999E-07 ERR= 0.0% DM/M= 1.1357E+00 ELAPSED TIME= 1825.74 s REMAINING TIME= 987.40 s Is it ok ?
  8. what is the effect of penetration and intersection on results ?
  9. i want revolute joint without any movement .ie. only to transfer load ?
  10. ank

    Hourglass

    We have to check hourglass energy for under-integrated elements ?How much it should be ?
  11. Something like this. sorry for bad drawing.
  12. As I can apply conc. load on nodes if I want to apply force uniformly I need to apply pressure load but pressure act perpendicular o surface direction.If I want to apply uniform load on a surface in particular direction?
  13. if i wanted to apply a uniform load on a surface in a particular direction then what i need to do ?
  14. I couldn't get why is it so? If force is zero at 0.005 and onward, I expect no deformation beyond that point. Why am I getting further deformation?
  15. Dear all, Please see the attached video and image. I am not able to understand the deformation behavior of the model. My load is transient (plot is attached). Initially from the zero position the model starts to deform in the direction of load which is pretty understandable. But at the end of the video the model could be seen deforming in the direction opposite to what is expected. Would anybody please elaborate why is it happening? What care should I take if it is because of some damping issue? P.S. - The deformations are scaled up by the factor of 500. P1.avi
  16. i think instead of max in case of shell element if we apply average then it is more comparable.
  17. what is required and which one is more correct ?
  18. Hello Everyone, I have been trying since very long on this problem but couldn't find a proper solution. I am experimenting on simple models to see whether the load between the shell and solid is transferred correctly or not. I have considered following three cases: A plate (100 mm * 100 mm * 8 mm) modeled completely with hex elements Same plate modeled completely with shell elements Half of the plate modeled with hex elements (from fixed end) And remaining half with shell elements The actual problem is the 3rd case, and to verify it's results, 1st two cases are being studied. I have tried different approaches (such as with skin elements, tie contact, penetration) but the answers were not matching with the 1st two cases. [The max. von mises stress in the 1st case =5.2e-1 MPa , and max. displacement in 1st case = 1.43e-2 mm ] The plate is fixed with a cantilever support and the force is applied at the free end (shown in the attached force - time graph ) Anybody please get me solved the .hm file attached herewith in the radioss solver. I also want to solve and test the results using RBE2 and RBE3 elements, but I don't know how to use them at the join between 2D and 3D mesh in my case. It would be of great help if the use of RBE2 and RBE3 would be demonstrated. ScaledUp_2D-3D_8mm.hm
  19. QUE: Why and when do we go for stress (t)? In my case, when I attach 2D shell to the hex meshing, I notice von mises (s) stress is much lesser in shell portion as compared to the hex portion. When I select Stress (t) and go for von mises, I find comparable stress values in shell part as that of the von mises (s) stress of the previous case (in the solid part) . What does it mean? Please explain. Does it mean when we have to see the stresses of the shell part, we go for the von mises in the stress (t) option? You said we use von mises stress is when we want to check when my failure may occur. Which von mises stress do you mean by that? Von mises (s) or the von mises option in the stress (t) option? [Actually I have an assembly containing solid shell parts].
  20. Stress tensor also having vonmises ?
  21. Hello Everybody, I am trying to experiment with a 4 mm thick plate (100 mm length, 50 mm width) having cantilever support at one end and a dynamic force applied at the other end. The .hm files and the force curve is attached for the reference. I have two cases: 1) The plate meshed completely hex elements (8 noded hex) 2) The plate meshed with the shell elements (4 noded quad) The force is applied at 26 nodes of conc. nature as shown in the figure I am getting different contours in both the cases. Why am I getting so, please explain? 2Dto3D_OnlySolid_4mm.hm 2Dto3D_OnlyShell.hm
  22. I am performing stress analysis of component assembly having a solid block and a shell plate connected to each other.My question is what is the difference between stress(t) and von-mises ?
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