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Victor
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I have feeling this might be easier with a hand calculation but I don't know how. 1. The easiest way is thin beam elements so that their bending stiffness is very small. You might need to artificially increase the stiffness to keep the diameter sma…
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This poor load distribution will be fixed in version 8.
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Yes, you can do it the same way on a displacement constraint. This will need the CCX solver.
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You can define the load as a function of time using a formula or table. Probably a linear increase then linear decrease would do, in which case, choose the Table option in the load window and enter 3 (time, force) pairs to identify the initial, maxi…
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The easiest way is probably making a table in a spreadsheet and copying and pasting it into the Z component box on a force load. You could also set up an approximate step function using exponentials or something but that might turn into quite a mes…
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The values at the nodes should always be non-negative. But the contour plot for values between nodes is calculated using the elements' shape functions which, if they're quadratic, allow negative values. It's partly a graphics problem (quadratic inte…
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It sounds like snap-through buckling which you usually can't model completely with Mecway or CalculiX. You would be able to deform it up to the point where it snaps through, but probably not the post-buckling behavior after that. If you havn't alre…
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It looks like it's working OK. A possible reason is that the node values are misleading or meaningless for a complex space frame like this because they're an average of the values of all elements sharing each node. Use the element values, not the n…
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Yes, you should be able to have no bending like that. Check the little cylinder symbols on the ends of the beam. There should be 3 at the ball-joint end and 1 at the clevis end oriented the way the clevis pin would be. If that doesn't help, can yo…
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Hello Gary Mecay doesn't have materials with damping included as a complex elastic modulus. What it can do is: * Discrete damper element (dashpot) * Rayleigh damping with different coefficients per material/layer. * Possibly viscoplastic mat…
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The internal solver is limited to 16 or 32 GB because it uses the LP64 programming model with 32 bit array indices. I don't know about CalculiX but it could be the same.
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No, sorry. If it's really hard, you could edit the .liml file directly.
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You could use constraint equations. I don't quite know the answer but here's an approach similar to what bonded contact uses but without coupling rotation: Start with the nonlinear constraint that the initial distance between the nodes is equal to …
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In some cases, you can select the longer edge and use Mesh tools -> Refine x2 to split it into two. For edges where the ratio of number of elements isn't a power of 2, you could apply that to a subset of the elements and move the nodes around to…
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> I was able to open the ".frd" directly late yesterday, but the model looks like an origami project gone wrong. From that description, it sounds like the 3-digit exponent problem which happens with some builds of CCX (possibly including the on…
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Not guaranteed. Mecway only supports some common DXF shapes as listed in the manual. Though a structure like this is probably going to become LINEs which are supported.
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Several things are unclear: Is it the internal solver (not CCX) that can't solve, or is it CCX run through Mecway? I'm concerned if there are models that can run in CCX from the command line but not through Mecway. How are you opening the .frd fil…
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DXF would usually work for this but apparently SW didn't export 3D DXF in 2011 but maybe does now? https://forum.solidworks.com/thread/50774 Here are some suggestions for exporting a list of point coordinates. You would be able to import that as t…
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My basic understanding of MFRONT is that it generates a dynamic library for a user defined material, which CCX links to. Is that right? I imagine you could already use it with Mecway by entering the material card in CCX -> Custom model definition…
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You're right that you don't need to do the thermal analysis first - that's for obtaining the temperature field in cases where you didn't know that in advance. While not a tutorial, the VibratingMembrane.liml sample file described in the manual uses…
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I don't think TIE is right for this because, as you found, it moves the nodes before solving so it doesn't impose any stress. The moving of the nodes isn't a feature for when you want to move things. It's there to make up for a shortcoming of the TI…
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I suppose element thickness in the direction normal to the surface but really it should be the thickness of an extra layer of imaginary non-space-occupying elastic material you can put between the surfaces without worrying that it'll deform signific…
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Making linear tets and converting to quadratic with straight edges is the same as what the automesher does when Fit midside nodes to geometry is turned off. It's off by default because it tends to make bad elements with the default element size sett…
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In this case, you can ignore the error message and leave the von Mises failure criterion active for the CCX solver. The error message is just trying to warn you that it won't be used. I see now that it should be more clear that it's simply going to …
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I don't know much about this method so it's hard to say at the moment. I've added it to my list but it seems like low priority. Version 8 should have a formula function in the postprocessor which might enable you to set this up yourself from the loo…
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Any luck with rigid body? I see what you mean about reading the manual. It explicitly says shells aren't allowed so I've added an error message to Mecway if you try to use *TIE with shells or beams. I did find that it seems to work OK as long as t…
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There's no special material for reinforced concrete. You might be able to simulate it using a laminate. I don't know how you'd convert rebar to an equivalent stack of orthotropic materials though, or even if it's possible in general.
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I'd like to isolate what's going wrong here because it sounds like a general problem. If you can post or privately email me the .liml file, that would be helpful. Maybe I need to put in some warning about this.
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It's probably too coarse a mesh. The yield calculation is done at the integration points inside the elements but the displayed stress is extrapolated to the nodes so it can be higher. Von Mises stress exceeding the yield stress frequently occurs for…
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Would it help if there was an option to generate .csv with the localized Windows decimal,thousands,csv symbols? I suppose commas and dots are a problem there too?
