Hi Tim, cool project.
Take what I'm going to say with caution because I'm talking from memory.
I think there are two solution methods for harmonic analysis: full and mode superposition.
With full method you can use non zero harmonic applied displacements, but with mode superposition you can't...
Read point 21.6.1.2 in the mechanical APDL technology demonstration guide and the help about UPGEOM command.
That example shows how to introduce initial imperfections (a combination of 10 factored mode shapes) prior to nonlinear buckling analysis.
You'll have to do the same but with just one...
I don't understand your equation, but you can retrieve all the elements from the stress and strain tensors with *VGET in the form of vectors.
Then you can operate with those vectors with *VOPER
And finally you can insert the result from the solution vector into the database with *VPUT (you have...
You have to rename the dimensions from within solidworks. If you edit a part of the assembly, then edit a sketch and click on a dimension you can change its default name in the "primary value" box. Rename it to DS_1_width for example. Do the same with all the dimensions you want to convert to...
Regardless of the meshing issue, I don't think you can apply cyclic symmetry to that model. I mean, if you apply cyclic symmetry the rail and the contact would also be repeated every 20 degrees.
When you are dealing with solid elements (no rotation degrees of freedom) the frictionless support is...
Have a try with this macro, it seemed to work for me.
I'm sure it can be done shorter and cleaner but I'm brushing up on my APDL skills
The results will be written to stresses.txt
I've added a third column to indicate the load step in which the maximum von mises stress is achieved...
