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Victor
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Comments
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You could try S8R instead of S8. I think that might perform better but I'm not sure about thin-walled structures in particular. It's now under CCX -> custom element type. The stress near the clamp presumably won't be correctly predicted by the t…
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Yes, those are limitations of it, unfortunately. It's quite a low-level tool that's not good for local refinement and the R,S,T directions depend on the element's node connectivity which aren't necessarily related to the U,V,W element orientation co…
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The procedure is similar to coupling thermal to mechanical for thermal stress. 1. Solve with DC current flow. 2. Add power density to the solution. 3. Switch to a Thermal analysis type and use Transfer internal heat generation from solution under Lo…
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Either solver would do for the thermal solve. Then yes, switch to Static 3D or any mechanical analysis type that allows thermal stress. That will have to be CCX though. Define the temperature dependent Young's modulus using CCX cards.
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While I don't know about RISA 3D specifically, there are a lot of formats Mecway can import nodes from. Here are the ones that other FEA software might be able to export: * .dxf POINTs become nodes. What settings are you concerned about? Just try…
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Thank for working out those shear components. I checked all 6 of them on an arbitrary shaped model with an arbitrary stress state by: * comparing to stress in global coordinates in the XZ plane, and they're all the same as that on at least a coup…
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You mean a way to make existing formulas available to other files? I'll try to make them work with Import but for now, you can open the .liml file with a text editor and copy and paste them between files. A formula looks like: m sqrt…
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Do you mean that it imports with File -> Import? Or that it can be used for the loads and constraints too? In the first case, probably. I think it's just my oversight that it doesn't get imported. In the second case. It seems more complicated. …
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It seems to fit more than about 60 000 characters. I don't know if it has a hard limit. It automatically wraps if the line is too long for the window.
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The only other way I can think of is *PRE-TENSION SECTION. See the CCX manual for details. It's fairly complicated to set up but it couples two nodes together and to a reference node such that if you apply a force do the reference node, it becomes t…
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Radial displacement is (x*u.x + y*u.y) / sqrt(x^2+y^2) which is the dot product of the normalized position vector and displacement. I think you can get tangential displacement with a cross product but not sure of the formula off the top of my head.…
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I don't know how but I've heard of people solving much larger models. Perhaps check on the CalculiX Yahoo! group.
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Thanks for the suggestion. It's one of those tricky things where the common use is a special case. Joining the ends would make the behavior of the tool more unpredictable even if it's more convenient most of the time. So I'm not sure really.
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Those are the units for x,y,z used in the formula. Line pressure is force per unit length instead of area. You can use either on the edge of a shell with the internal solver but only pressure with CCX.
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I've found the limit is typically around 300,000 nodes with 16 GB of RAM. I expect you would be able to go higher though. You can delete half the mesh and solve to see if it succeeds. The closest things to contact for the internal solver are: * …
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That's one of the usual ways CCX exits when the model is too big. I don't think it can use all of 64 GB of RAM unless you compile it specially. Did you see how much it did use? It might be limited to 16 or 32 GB. 900,000 nodes could easily exceed on…
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Not sure. I hope that there's another way to identify improper meshes like an exit code or error message or something. That'd be easier from my perspective.
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I don't know how changing material properties would help with allocate failure but maybe that somehow keeps it under the limit, or maybe it was by chance? There's no special rigid body without defining it through CCX cards, but you could use a very…
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One of the corners is missing. But that is weird that it silently generates the surface mesh. I didn't know that was happening.
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Node 7179 is part of the the very first bonded contact's slave surface Pipe_to_Tape as well as Pipe_Exterior_Master. So that's why it fails. An intersection between 3 parts all having bonded contacts on their common edge is limitation that you can't…
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I found that ran a few iterations then exited without a solution on 2.11 single threaded. I guess you'd have to reduce the mesh size. A major area is the interior where it probably doesn't need to be nearly as fine as it is. You could also replace …
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Does the right hand image show thermal transient? It should be available. Here's a simple example that solves. However, this will only work in the same way that it does with the internal solver. To get radiation between surfaces, you'd have to modi…
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You would also need a gravity "load" and a constraint somewhere, such as fixed support on the bottom. You're also welcome to upload the file to make it easier to see what's happening.
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Look for multiple constraints sharing that node and see if they're either physically conflicting or breaking Mecway's rules. Thermal constraints include fixed temperature (one node cannot have two different temperatures at the same time) and bonded …
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I'm not sure why that's warned against. It might be that it sometimes generates solutions with time steps but I can't see that happening. It does seem to work OK if you ignore the warning though so as long as you're confident that CCX is alright wit…
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Hello Thanh. Could you give more details about what you're stuck on? Or you can have a look in Help -> Tutorials which shows examples of applying boundary conditions.
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It adds that option to the File menu, which presents files and folders as submenus for importing, rather than going through the File -> Import dialog box. It's a special feature for one customer who used Import a lot to save them navigating the …
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Do you really need to model both surfaces or can one be ground? If you only need one then elastic support might be OK for the stiffness. It's springs normal to the surface. If you need both surfaces then you might have to put individual line2 spring…
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In version 10 which is now in beta, you could do a surface integral (Solution -> Surface integral) over the surface of the section, then divide by its area to obtain mean normal stress. In version 9, you could make a very thin section and use So…
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Something's quite strange about those two strips that are bending in the wrong direction. I isolated one of the offending parts but still can't work out what's going on. Refining the mesh does solve the problem, but so does changing the thickness of…
