Hi Mads, really good. Do you have an idea how to apply the pressure only on a portion of the tube. I have the same conditions as you but I apply the external pressure only on a short ring. I don't find how to do that. Thanks!!!
Hi Kerstin-Evelyne. Sorry about this late reply. I don't get many comments on this video, although quite a few is watching it. You need to model the cylinder with more extrusions. This way you get more surfaces. You can apply a pressure to those surfaces individually. Remember to bond the surfaces using a "surface to surface contact" found under contacts in the top ribbon. I use the manual one. Hope this answers your question. BR Mads
@@madshoeirasmussen2786 Basically, run an eigenvalue buckling analysis for a certain load and then use the displacements/modes to run a second non linear analysis. I think it may not be possible.
That more or less what the system does. First the mode shapes are found by means of a modal analysis. Then the mode shapes are created and the critical load is found by iteration. Remember that the magnitude of the deflection is irrelevant. Buckling is an unstable fenomenon.
Hi Mads, really good. Do you have an idea how to apply the pressure only on a portion of the tube. I have the same conditions as you but I apply the external pressure only on a short ring. I don't find how to do that. Thanks!!!
Hi Kerstin-Evelyne. Sorry about this late reply. I don't get many comments on this video, although quite a few is watching it. You need to model the cylinder with more extrusions. This way you get more surfaces. You can apply a pressure to those surfaces individually. Remember to bond the surfaces using a "surface to surface contact" found under contacts in the top ribbon. I use the manual one. Hope this answers your question. BR Mads
Nastran tool is not present in my Inventor Pro 2020?
You need purchase it seperately or buy the design suite pack
Hi! Is it possible to run this same analyses with a prestress load ??
What kind of prestress?
@@madshoeirasmussen2786 Basically, run an eigenvalue buckling analysis for a certain load and then use the displacements/modes to run a second non linear analysis. I think it may not be possible.
That more or less what the system does. First the mode shapes are found by means of a modal analysis. Then the mode shapes are created and the critical load is found by iteration. Remember that the magnitude of the deflection is irrelevant. Buckling is an unstable fenomenon.
@@madshoeirasmussen2786 You are right, but do i have the option to select a mode and superimpose a fractional value of the displacement at that mode?
@@drury2d8 i don't know how to do that. But buckling is linear. So the result would be the same no matter magnitude of the deflection