Hi Jack.
What do you mean by "default values for A01 and A10"? Those two values do not have a default. (Okay, maybe Nastran defaults to 0.0, but that is meaningless.)
If you do not have real material properties, you are wasting your time trying to use a hyperelastic material properties. Another customer said the following in regards to determining the hyperelastic coefficients:
- Data from many suppliers is unreliable.
- When labs provide testing for FEA, they have to tweak the constants so that they work. (To me, this implies that even with sufficient lab test results for tensile, compression, shear tests, and so on, you may still need to adjust the constants.)
- Try the following "balanced" Mooney Rivlin constants. A01=0.15; A10=0.6; D1=25. If the model runs with these constants, then the loads, constraints, and mesh are probably okay. If the analysis fails, the mesh, contact, etc is causing a problem, and the analysis will not run with real material properties.
But of course, you do not want to use the "balanced" Mooney Rivlin constants for the final analysis because who knows how closely those constants apply to your material. If you have the stress-strain data suggested in this article, you can input the stress-strain data. See How to enter hyperelastic (rubber) materials in Nastran. If you do not have the required stress-strain data, you should just use an isotropic material with a Poissons ratio set to 0.48. (Real rubber has a Poissons ratio of 0.5, but that value does not work in a simulation.)
I tried with isotropic properties (E=435 psi from material library, Poissons = 0.48) and a coarse linear element mesh. The analysis got to 47% complete before it failed. It may require a much finer mesh, or the amount of compressive strain may be too large for the analysis to handle. I suggest making the model 1/10 the length so that it runs faster. There is also half symmetry about the YZ plane, so cutting it in half would also reduce the model size. (Once you get the small model to run, you can run the full model overnight if you want to show that result to a customer, for example.) If using a parabolic mesh, you will want at least 2 elements through the thickness of the door seal for the final run. If using a linear mesh, you want 4 or more elements through the thickness. (I do not know for sure, but I'm guessing that linear elements are less prone to buckling than parabolic elements.)
John
John Holtz, P.E. Global Product Support
Autodesk, Inc. If not provided, indicate the version of Inventor Nastran you are using.If the issue is related to a model, attach the model! See What files to provide when the model is needed.