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Victor
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Judging from the number of equations, it looks like you might be bumping up against a memory limit and that might be causing inconsistent failure or success. The "Solver reports *ERROR" message is simply parsing the error message shown the CCX outp…
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I don't know a lot about the ASME code but are you asking for it to do stress classification to identify secondary stress Q then sum it with Pl and Pb? I think that might be difficult for general purpose software because it depends on quantities lik…
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That or similar errors can happen with node rotation or fixed support, moment or force (on faces, not nodes) on shells in some cases, particularly if they're curved. Bonded contact can also fail if it's sharing node with another bonded contact or c…
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Oh, I was a bit wrong on that. Because of the special meaning of that load, DOF 1 here means the pretension direction, not the global X direction. It can be oriented any way and it's still DOF 1.
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I'll quickly try to answer this, hope I don't step on your reply Sergio: *CLOAD 48393,1,-1000. * CLOAD = concentrated (point) load * Applied to node 48393 * DOF 1 (X direction) * -1000 N. * This load has the special meani…
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The *TRANSFORM is likely because of a frictionless support on a surface not aligned with the 3 global axes. The *AMPLITUDE is likely from a time-dependent force. If these two things are sharing nodes, change it so they aren't. One way is to replace…
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Yes, this is a bit of an inconsistency. Complicated data like lists and formulas don't update when you change the units. So if you want to change the units for display while keeping the physical meaning the same, you have to manually edit the number…
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Could you please attach the .liml file or a screenshot showing the constraints? At a guess, it could be that the constraints are only defined in one direction so they can't support forces in any other directions. You need 3 displacement constraints…
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Yes, the default value is based on the materials of the face(s) at the time. It's just a rough estimate that will often get a solution, but you may need to adjust it again. I usually adjust it by an order of magnitude or two at a time. The theoretic…
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Hello German. Unfortunately, I won't add this feature to the next Mecway. It turns out it's complicated and a bit risky to try to decide which nodes belong to the additional cyclic symmetry segments, especially since there could be more than one. Th…
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That would be true for mirror symmetry, but static cyclic symmetry requires displacement (in cylindrical coordinates) to be equal on both sides, but not necessarily zero. Here, you can see the opposite side has the same circumferential displacement …
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I can't see anything wrong with the cyclic symmetry definition in your original model, Hooshsim. According to the CCX manual, ELSET is only used for generating the output segments so I think it's harmless to omit. Combining the 3 pairs of surfaces …
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If you're not worried about privacy, there are web services where you can convert MPEG generated by Mecway's animation button -> Save video to file to GIF. Just Google "mpeg to gif". But beware that some of these sites publish the content people …
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There's a couple of dozen but I doubt you actually need all of them for only PARDISO. Here's a sort of explanation but I still can't quite work it out more accurately than "everything in redist/intel64_win/mkl": https://software.intel.com/en-us/art…
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Not that I know of, sorry. It's a feature I hope to include in a future version.
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Currently, the only way is to adjust the range of the color key scale. If you exclude the highest magnitude ones, it lengthens all the others. Use the sliders next to it or select the magnitude from the outline tree then right click a selection and …
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A couple of things I've recently found: Although the minimum set of dlls JohnM listed are OK, they're the default ones for the lowest spec CPUs. If you include all the other dlls from the MKL redist folder too, it automatically loads ones that are …
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Hello Daniel 3D shells are always plane stress and the plane strain option is disabled. 2D continuum elements are plane stress by default and you can change it to plane strain by turning that option on. It should be enabled if the Shell/membrane m…
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File -> Import generally doesn't import solutions. A workaround is to use File -> Open to open the .frd file then Import to import the model again. You might also tell Mecway that your program is CCX (Tools -> Options -> CalculiX) so it…
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I think that's right. The entire stress state should be uniform throughout, including the principal directions.
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You won't be able to simulate the failure itself in Mecway, which I guess is what those wave speeds are for? If the material has some load rate dependence, I think you can simply set the properties to what they would be for the load rate you're usi…
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Thanks for suggesting that again. I'm not sure about it at the moment but it's on my list to sort out.
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Hi Dave 1. It turns out the large displacement is actually a rotation because of the unconstrained rotation you identified. But the point displacement constraints are going to cause point reaction loads too which I guess isn't what you want. I'm no…
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The Displacement and Node rotation constraints do that. Each one constrains a single DOF. Choose one of the predefined orientations (X, Y, Z) to populate the top row of input fields and they will behave like traditional global DOF constraints.
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I can't promise but that is a feature that people have asked for before and I realize it would be valuable.
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Thanks for the suggestion. I probably won't do that soon because of other priorities. However, version 13 will probably have an API which you would be able to use to export data in any custom format.
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If you use Gmsh on a STEP file, then usually the same-shape surfaces end up with the same mesh so you can merge them together. You can download Gmsh from http://gmsh.info/ and then connect Mecway to it and use it through Meshing parameters -> Gm…
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In these models, the parts have compatible meshes and share nodes so there's no need for bonded contacts. If you use STEP files and automesh them, that won't usually be possible (though with Gmsh you usually can). If the different parts are the same…
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That's an odd omission. I'll get Mecway to generate the data for the other segments if it's safe. I'm wondering if perhaps there's a reason CCX doesn't do it.
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Here's some steps to get started. From this, you can solve it and get some kind of solution but it doesn't yet have: * Holding forces * Plastic material. See manual 14.1 Custom model definition for an example. * Friction. Set it in the contac…
