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Victor
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@disla, @kuhl, I wrote a script to do the "hollow" operation on shells here: https://mecway.com/forum/discussion/comment/7097/#Comment_7097
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Converts shell elements to line elements along their edges.
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The ones in the list are all text format single numbers - either double precision or integer. As for their meaning. I'm, not sure there's really one source. Most or all are also parameters for Netgen's nglib interface, so you can probably find them…
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I think you can define that by writing the *BEAM SECTION card yourself in CCX -> custom model definition. See CCX manual for details. But if it's really just a simple beam, probably easier and more accurate to use solids.
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@disla, yea, I agree you can just use mass for rotational inertia, like how reality does it. But be careful with just two of them because it'll behave differently for rotations about other axes. Does it even make sense to have a remote rotational i…
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Sorry about that. For the internal solver, you could use high-stiffness beam, truss, or spring elements to support a remote node with rotational inertia.
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Use nonlinear analysis because the X-displacement is a nonlinear function of the load.
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Could you at least show me the whole outline tree, so I can see what things are present? Yes, once it's there, it'll be now evaluated when it solves.
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It's apparently instantaneous for me with a 180 000 node model and 50 000 constrained nodes having reaction force summed, so maybe something else is breaking it. Would you be able to send me the file privately?
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Oh. It might be too inefficient evaluating it. I'll have a try with a big model. Did you have a lot of time steps in the solution? It finds it for all of them so in those cases it'll be slower than before.
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Here's an example. The mass's node doesn't appear in the solution but it still exists for the solver.
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Yes it's meant to do that. It doesn't get stuck when I try it. Do you mind describing the steps to reproduce the problem?
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Which OK button? I might have to rethink the outline. Though don't forget you can make it thinner in Tools -> Options.
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Haha, the fix for slow display of bonded contact was to not display the little circles and lines, which I did for one version. But people didn't like that so it's back The slowness there is because it's matching up the nodes, faces, points on face…
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Ouch. Sorry it's been such a time-waster. I didn't quite realize how serious it was until you mentioned 65 hours. The not hiding model edges is intentional. Some people have said they want an awareness of where the non-hidden parts are so I thought…
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The previous versions would apply each term of each MPC to the system matrix by making a dense copy of a couple of entire rows and operating on every value, despite the matrix being sparse. That lead to millions of redundant multiplications by 0 for…
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@kuhl, I've fixed the unreasonably poor performance for bonded contact in static analysis in an update here https://mecway.com/download/mecway200_Beta3.msi (v20 beta 3) For example, a 100 000 node model with 12 000 bonded contact slave nodes that u…
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Fair enough about CCX shells. Some of their problems are related to rotational DOF and transformed (non-global-axis-aligned) constraints and often there are alternatives to those. For bonded contact, the elastic option is the most reliable for shell…
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@Sergio found a way to make compatible meshed with Gmsh, described here https://mecway.com/forum/discussion/808/conformal-meshes-with-gmsh Sorry it's so slow. The delay is in generating the MPCs and is caused by the inefficient way it accesses the …
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Thank you for bringing this effect to my attention! It might look like I already knew what I was talking about but I spent a while identifying the problem after trying to refine the mesh, change the Poisson's ratio and stiffen the free end before re…
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Zero displacement will have the same effect as fixed support for solids. I put something like a fixed diaphragm constraint (Y and Z constraints on the whole surface, and X constraint on one node for rigid body motion) on the shells and solids and n…
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I've only had a brief look at it but I'm guessing it might be the fixed supports on the solid and shell models that constrain warping at the base. The torsion constants for beams assume they're free to warp regardless of the constraints, which is p…
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If the .step file is at the same or lower level in the directory tree as the .liml file, then Mecway only stores the relative path so you can move or copy the whole structure to somewhere else without altering anything. If it's anywhere else, like …
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Good stuff. I need to incorporate this into Mecway's UI eventually. Is frequency response.liml this? https://mecway.com/forum/discussion/comment/5029/#Comment_5029
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Use Select nodes mode and you can click on them to show the value.
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Indeed. Thanks @disla.
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Set the solver to CCX and analysis type to Nonlinear Static or Dynamic 3D, then large displacements will be treated properly.
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Remove any loads that trigger stress-stiffening and it outputs stress in the same way as static analysis.
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I'm not sure I'll be able to do anything unless more information comes up or I can reproduce it. Save and Save As are almost identical except for one showing the file picker dialog box and updating the recent files list. The way it fails is consist…
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CCX doesn't generate output for t=0 so the first time step is already 1 or 2 minutes in where it's supposed to be hotter.
