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Thanks Marco. I can reproduce it now. It only happens with the gradient contour plot option.
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To be honest, I don't know much about it besides the formula used by CCX. Here is a simple example whose solution matches that formula. You do have to define E, but that's on the Mechanical tab of the material properties window.
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Stefanos: Yes. I'll contact you by email in a day or two. Marco: Thanks for the bug report. I'm not able to reproduce it so could you please give more specific steps and/or take a full screenshot showing model and any selections? When I do it, it s…
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In version 7, node external force (including reaction force) x,y,z components are called FORC_F1, FORC_F2, FORC_F3 respectively and should automatically appear in the solution. The units are always Newtons. In version 8, they're called external for…
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Thanks to your request previously, in version 8, you can show cylindrical coordinates by entering the transformation formula in the postprocessor. There's an example for radial displacement in the manual.
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Yes. Just beware that the setting clears itself when you close the program. In v8, it's under Loads & Constraints and is persistent.
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Barrti, just a comment on the 8-node hex's. Are you using reduced integration as Sergio suggested somewhere way back? He found it didn't help with hex20 but it's particularly important with hex8. Without that, 2 layers is probably too stiff. That mi…
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I think you're probably onto it with the knots. I don't understand them well enough to say though. Generally, all the 6-dof elements in CCX are a bit flimsy and it sometimes fails in surprising ways. I've seen the geometry of connections between ele…
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I'm not sure why this happened but adding a dummy element with zero density to the node with the moment makes it solve. I also turned on automatic time stepping which helps it get further into the solution but it only rotates about 45 degrees.
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OK German. I'll make those changes unless I run into big obstacles. Thanks again for your very thorough and competent work on the manuals.
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I'll look again later but you might need to use a force couple on an additional element instead. Force on the wheel works.
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I agree that showing other types of selection in the list is inconvenient but it's the same behavior as all the loads and constraints that only support one or two types of selection, so that's a fix for another day. Using component names is a bit t…
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v7 had CCX 2.11 too. I haven't tried to compile 2.12 or 2.13 yet.
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Hi Sergio, thanks for the detailed comments. 1) The "displacement" tree node shows arrows but the "magnitude" one under it shows the usual contour plot. This is something I'm worried about because it's a bit harder to reach for the common case. Do …
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All those settings look pretty good. Two suggestions: 1) Use a prescribed displacement instead of a force. It looks like the strip has reached yield across the whole cross-section so maybe it's collapsing and can no longer support any more force fr…
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Update: beta 2 mecway.com/download/mecway80beta2.msi Bugfixes Geometry didn't display or mesh. Samples and Tutorials folders weren't shown in File->Open Incorrect localized number format when saving files. Improved error message for out of memo…
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Thanks for reporting that bug, marco. I'll release a fix in a couple of days.
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Version 7 doesn't do that, sorry. You'd have to solve the configurations one at a time and copy each csv file away before solving the next one.
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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.
