I'm revisiting my analysis from my discussion "Large Deformation FEA". Though I received a lot of useful info, I'm still struggling to get accurate results.
Attached is the file I'm analyzing as a contact analysis assembly.
This screenshot captures most of the details (mapped mesh constraints, contact surfaces, total load at point, symmetry, displacement):
It also shows that this test failed with my given material properties. It will run with other material properties, but I haven't gotten anything close to real results.
Also, when I run this analysis, I get odd results and it's still taking my computer a while to solve this with mapped mesh and only one part with nonlinear material properties:
I assume it's because my contact point at the top is sharp that it sees a little interference and then overcompensates.
Have you all seen issues like this?
Any suggestions would be greatly appreciated.
My $0.02 is to avoid including contact if you can given that you're doing a LDA. Contact with LD formulation is somewhat new to Simulate and isn't the most robust. Another issue with this model (when compared to your physical test results) is that you might need to account for a sharp change in the stiffness matrix with the snap through effect, which appears to be bugged at the moment.
I forgot to post this in your other thread, but I did make a more refined model where I removed the constraints that you were using to represent the tube and replaced with them spring elements and weighted-links. The model still needs more work (such as getting a better approximation of the contact area between the tube and the support).
Thanks again, Shaun.
It seems like eventually I could get an accurate result with methods like you've done, with more fine tuning.
Looking at the bigger picture for me:
I'm using this 'simple' test in hopes of validating this software for more complex assemblies. Is this a realistic goal? Will I be able to achieve a strategic process of applying constraints, loads, idealizations, and material properties that will get me close (maybe +/- 20%) for nonlinear, large displacement assemblies?
A quick look at the pictures and my £0.02 x $/£ exchange rate ...
Similar log file error to ones I have encountered which for me meant I 'ran out' of stress-strain curve; no more curve to work along as values are too high.
If you are to use contact, I would be tempted to bring the components into contact in the assy first. The initial large movement (zero stiffness gap), surfaces may 'miss/overshoot' and will make iteration look as if oscillates; taking much longer.
Again, if using contact, I would consider small rounds rather than square edges. Though this means more fun meshing and more contact interfaces; stresses/strains may be high but more 'sensible'.
Thanks for the input, Charles.
I have the components of the assembly mated (edge to surface) so there are no gaps initially. I guess I assumed that when the program uses one of it's material laws, (linear, power, or exponential) that it would carry it out as high as needed, sometimes getting unreasonable strain values.
Your thought of using rounds rather than corners is very good. That makes sense that it could help for convergence and run time.
I think Creo will interpolate within but not extrapolate beyond UTS. Raising the UTS may get it to continue. The large resulting strains will require finer mesh and longer run times.
Can anyone form PTC tidy up this vague area of my understanding?