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Victor
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Comments
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Yes The Buckling 3D analysis type is only a linear analysis and can give an idea of the mode shapes but for something with large prebuckling deformation like I expect this would have, it might not be accurate enough. As safer way is to use the Non…
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I won't add *NODE PRINT unless/until Mecway can ready the .dat file it produces.
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Yes. You can open a .dxf file and mesh it with Mesh tools -> Automesh 2D. If the meshing fails, it can be because it's not really the closed boundary of a shape(s). It can also be a bug in the mesher which happens with some shapes and the automa…
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With the next version, I'm reworking the postprocessing to make field variables optional so that adding more like this, and hopefully user-defined ones too, will be easier. So far, I have been reluctant to add things like this with niche applicabili…
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That's very weird. Perhaps in Windows explorer: Refresh the display with F5 Turn on showing Hidden items. It also sounds like UAC virtualization where only the applications that created the files can see them. https://blogs.msdn.microsoft.com/oldne…
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You mean edge faces? That's often easier by selecting nodes first then changing to Select faces mode. At least for straight edges. Paint selection is still not much use for those unfortunately.
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It sounds like gmsh didn't generate any output. Perhaps take the .geo file and open it in Gmsh directly to see if it shows errors.
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For now, all you can do is zoom in and out since the selection size is a fixed number of pixels. I tried some automatic size changing but that turned out to be a nuisance. Can you describe your use case a bit more? Maybe it needs an old fashioned d…
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With Mecway, after you solve it, go back to the model and use Mesh tools -> Transfer displacements from solution. This makes the mesh deformed and you can save it in any of the existing formats like STL or .inp/etc. that has a simple node coordin…
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A funny workaround to find a very high maximum is with the deformed view. Change one of the field variables from displacement to the stress value and set the others to (none), then the maximum will stick out like a spike. You also have to tweak the …
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Thanks for the suggestion. I've added it to the list but it may come behind other file formats, if at all.
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I want that too but for now it's too hard so no, or at least not yet sorry.
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Cheers and no problem
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local max/min with a button sounds like a good idea. I should get that in for version 8.
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No but it really should be there. I'll add it to the next version. Thanks for the suggestion.
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Yes, all correct. It looks like it should be on the Z-axis to have any effect because there's no rotation about the X-axis. And yes, the massive beam elements have their own rotational inertia which allows it to solve. Otherwise "I" would be zero in…
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I see. That makes a lot of sense. Yes, I'll also get the refine x2 to update the nodes. This is a common problem.
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This kind of geometry with thin parts with lots of exterior surface is especially bad because it has more faces to render compared to the number of elements. As Sergio said, turning off element edges can help a fair bit, so can turning off "Show mo…
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To view the interior stress, use the Cutting plane slider at the top-right of the toolbar. To get the data in table form, you'd have to align some nodes into the plane you want before solving. You can then make a node selection of them and that'll …
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I'm trying to keep the manual fairly minimal and factual. Targeting a broader audience is more difficult to get the balance right.
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Oh, thanks for spotting that bug DaveStupple! It'll be related to the DPI setting in Windows. I'll fix it for the next version.
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Since this is a statically indeterminate support, the elasticity of the parts is important. By using spring constraints, you're substituting the stiffness of the gantry and its rails with those springs. That might be OK if you have a way to find wha…
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Two things: 1) There are two meshes over the top of each other. Select the Default component which doesn't have any constraints and press delete to delete its elements. 2) The prescribed displacement is too aggressive. CCX reduces the time step si…
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It still only works with solid elements. Though that includes the solids generated by CCX from shells and axisymmetric models as long as their nodes are properly connected.
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Thanks for telling me that about the red line. I never considered that possibility before! It's not an error, though when the text is red, that is an error. Right click it to see the error message. In Mecway, each displacement (or node rotation) co…
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For nonlinear, use contact instead of compression-only support. You'd need to make a mesh of the platform too. It could perhaps just be a single big element. I don't know about your other questions, sorry.
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Use displacement and node rotation constraints to allow you individually constrain each direction. In the attached picture, I accidentally put in a redundant Z constraint which I removed from the liml file.
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I see. I think it's at least partly because of an approximation in how the pressure load is applied in the internal solver - uniformly across the element instead of concentrated near the larger radius. They both approach the same solution with mesh …
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Once you have an elastic contact, it's already pretty much a complex nonlinear analysis, so I'd say, just use that directly. Shell shear force per length is enabled by Tools -> Labs -> Output extra shell stresses. However, the values are some…
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This is tricky. I don't really know how to do that, or even if you can. *EQUATION only does linear equations, so if you connect displacements, they'll have the same problem of not rotating properly with large rotations. *MPC does nonlinear equations…
