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Victor
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Good points @German and @prop_design. Sometimes I copy requests onto Github myself. That's an embarrassing mistake with the more info label!
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The critical load is buckling factor times applied force. You can adjust the mesh according to the mode shape and a scaling factor using Mesh tools -> Transfer displacements from solution.
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* Set analysis type to Bucking 3D * Choose a Number of modes. I normally use 3 or 4 to get a sense of what else is around even though only the first mode would actually occur. * Set Shift point to something less than the lowest buckling factor.…
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Hello Nigel Case 1) You don't need tension-only if you know it will always be in tension. In either case, truss elements won't work because the pulling point is unconstrained in the direction of the applied force so no linear static solution is pos…
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The circles represent pin-joints which truss elements have at both ends, so they're free to flop all over the place. Usually, you shouldn't refine truss elements for this reason. If you really need to - eg, to capture bending of the members due to l…
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I prefer if feature requests go in Github https://github.com/victorkemp/Mecway/issues so they don't get lost and other people can upvote them (thumbs up reaction).
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STEP
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The next version (25) will probably have support for Alibre Design/Atom3D assemblies where each part becomes a separate component in Mecway. Not for general STEP files but I hope to find a way to achieve that because assemblies are quite important.
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The problem here is to find wrinkling so the elements need to be small compared to the wavelength of the wrinkles which is a bit unknown. Maybe it's too coarse? The CCX manual has an example of wrinkling due to shear in section 5.16 Wrinkling of a …
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Since displacement isn't proportional to load, you will need nonlinear analysis (Nonlinear static 3D and CCX solver). It probably needs an initial imperfection too, like some nodes moved a little. I couldn't find any wrinkling that way but I wonder…
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Not currently, sorry.
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They are supposed to have the same effect globally, yes.
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Contact stiffness is so low that it looks like they aren't interacting. Units are Pa/m but should probably be GPa/m. You can set the entire surface of the plate as contact face instead of a patch in the middle.
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Yeah, it's the condensed DOFs appearing in multiple equations problem. For example, x displacement on node 61 is the condensed DOF in both these equations: ... Change the order so the 1st node isn't the comm…
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@sofien_73 What you posted looks OK. A likely problem is that the node-dof pair that's the first term in each equation is the condensed DOF and is not allowed to appear in any other equation, nor various other constraints. For more than 2 nodes, th…
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You can use View -> Open cracks which separates coincident nodes. Another thing I sometimes do is Mesh tools -> Merge nearby nodes and check the total node count to see if it went down, then undo. Doesn't show you where they are but does show…
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Yea, it could use a tool to combine them when they're equivalent.
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It's not possible with the same mesh since a single node can only have one value for each variable. You can disconnect the members at the connections, keeping the nodes at the same location and then join the nodes with constraint equations (all 6 D…
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Oh, that's an unusually high number of separate loads (thousands). Mecway's not designed well for such fine grained detail. As @disla said, it slows down the display. I hope to improve this in future though. It looks like a lot of items can consoli…
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That's what the "Graphics detail during navigation" setting does for things like load and constraint symbols, selected faces, and thick model edges. Contour plot resolution shouldn't be an issue during navigation because it's not regenerated then, w…
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As well as contour plot resolution, these are some options that can speed up: - Choose banded in Options -> Contour plot - Turn down Graphics detail during navigation in Options -> General - Turn off View -> Show model edges - Turn off Vie…
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The threshold angle for displaying the thick edges is 20 degrees, which is coincidentally the same as CCX's threshold for introducing knots in shells. However, the way they each measure angle on curved elements might be slightly different so they mi…
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I guess that's the reason Guido once removed the use of knots in some places like beam ends where they seem better. On curves like this, I wouldn't consider it a serious problem because with mesh refinement, the angle between elements will go down …
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It doesn't have a report generator, sorry.
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Haha it is too! It's been great knowing you for so long Anthony. And thanks for your help with those mind-bending inertial forces, Campbell diagrams, finding so many bugs, and providing me with motivation to implement many features. Your work with p…
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Yea, CCX would require a unique *TRANSFORM on each node for that. Mecway 24 has a new feature which does this - Symmetry in Loads & Constraints. *EDIT: *TRANSFORM allows a cylindrical coordinate system which looks like it might work for this. …
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That look pretty much right. To keep it simple, I would eliminate scaling for everything except one value like this: Thermal tress reference temperature = 0 K Density = temperature, like (-1e9,-1e9) and (1e9, 1e9) instead of (0,0) and (500, 373).…
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Another idea is to vary the density rather than g. With CCX, you can define density as a function of temperature (just make it a linear function using 2 density/temperature pairs), and apply a non-uniform temperature field (defined by formula) on th…
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From what I've seen with beam elements, if there's a knot where you apply a moment or rotation constraint, then it uses that instead of mean rotation MPCs. So my guess is this avoids the <90 degree limitation on mean rotation MPCs.
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Forcing a knot at the loaded end causes it to solve for all angles, unlike the 360/180 degree convergences failures without? I wonder what the disadvantages of knots are. Maybe they artificially constrain deformation since they supposedly only allo…
