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With MKL, also do option 3) here https://mecway.com/forum/discussion/1012/improving-performance-of-ccx-solver which is copying over extra DLLs to enable CPU-specific optimizations which speeds it up over the basic set described with the source code.
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Hello bailey_rowland. That should work as you expect. Can you attach the .liml file to check for problems? Some ideas: Do the displacements match on the two parts? (use deformed view) If not, the bonded contact might somehow not be working at all.…
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There's a minimum element size of a few microns for CCX. You likely need to scale it up and imagine different units for everything to compensate, unfortunately.
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In case you find the liml format that Mishal suggested too complicated, you can also use CCX/Abaqus .inp format. Here's an example with 4 nodes, 3 beam elements, 2 force loads, and a partridge in a pear tree: *NODE 1,0,0,0 2,1,0,0 3,2,0,0 4,3,0.…
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For the elements being expanded to solids, you can add the OUTPUT=2D parameter to the *NODE FILE card so they'll appear as 2D shells in the solution and with the same node numbering. Add a CCX -> custom step contents containing *NODE FILE,OUTPUT…
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Could you be a bit more specific? You can model soil pressure that varies with depth by entering a formula in the pressure load. For self-weight, add a gravity load and specify density in the material properties. Use Nonlinear Static 3D analysis …
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Hello Yang That error message looks like it comes from this c code: if ((msgFile = fopen("spooles.out", "a")) == NULL) { fprintf(stderr, "\n fatal error in spooles.c" "\n unable to open file spooles.out\n"); } so it suggests some gene…
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This problem often happens when the temperature gradient is a poor fit for the quadratic elements. That often occurs at abrupt temperature differences like what you may have between the 140°C seal bar and the 20°C initial temperature of the lidding …
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I'm not aware of any cases where the internal solver gets stuck forever. It can take a long time at some steps but it should eventually either succeed or fail with an error message if you leave it long enough, which could be up to a day. Just a tho…
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Thanks prop_design. With a lot of help from you in finding bugs and advising on some domain knowledge.
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14.0 final released and on the download page. As well as the Spanish manuals, there are now also Portuguese translations at https://mecway.com/product.html
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Thanks. This has come up before. It's on my list so hopefully!
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Not easily. With CCX, you can add a *AMPLITUDE block. It's meant for time dependence, but you can just put a single value at any time (eg. 0) and it gets multiplied by all the loads that refer to that with their AMPLITUDE parameter which you also h…
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I seem to remember the usual behavior when it needs too much memory is to leave an empty .frd file and abruptly exit with no error message. Don't know about the log file though. Is it that?
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Yea, it's because of the solids like prop_design said. You can get the solution as shells though by adding this *NODE FILE, OUTPUT=2D in CCX -> custom step contents.
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@avscorreia Yes, major versions (12, 13, 14, etc) can all be installed independently.
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@Sergio. Yes, it's a bit of a compromise to use total strain instead of plastic strain. I've tried to make it clear in the UI to prevent mistakes though.
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@pberry, Thanks for the suggestions. All noted. @Vinicius_Petrucci For 1.png, you can use Extrude. But maybe number of copies input in Move/copy would be helpful. What I usually do for a huge number of copies is make several copies, then select a…
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@Vinicius_Petrucci Thanks for the detailed ideas. First suggestion: Mecway isn't really aimed at civil engineers, so I don't want to bend it too far that way. But Sergio has also asked for more convenient ways put similar material properties on lar…
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An additional thought - If the load should be distributed according to the area of the panel such as uniform pressure load a floor, then my previous suggestions are probably too complicated and the only practical option may be to mesh the panel exp…
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The linear Dynamic Response 3D analysis type can't model buckling. Use Nonlinear Dynamic Response 3D with the CCX solver instead. You'll have to change the elements to line3 for that too. I didn't get much different a result until I doubled the for…
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Load to panel nodes: * If the geometry is simple (axis aligned, not too many nodes), it may be practical to do it using constraint equations. * With the CCX solver, there's the *DISTRIBUTING COUPLING keyword which also requires you to specify t…
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You can remove them with Mesh tools -> Delete unused nodes.
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You can enter a function of x,y,z in a Temperature load like this:
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@drose. If you mean time points for dynamic/nonlienar/etc., you should be able to do that by manually adding the *TIME POINTS card for CCX. If you mean frequency "data points" (I'm not sure what that is) in a frequency response, it looks like you h…
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I agree it's a bit confusing. It means use the Isotropic option in the Mechanical tab. That's because it uses Young's modulus and Poisson's ratio from there. No UTS, sorry.
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Thanks for testing that @dculp. I hadn't considered the cost of the stress. Looks like it may be more useful.
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Here's an example. The changes are to replace *FREQUENCY 8 with *FREQUENCY 8, 1e8, 3e8 to limit it to modes between 1e8 and 3e8 Hz
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Add the PU variable to a *NODE FILE block to get phase and magnitude like in the attachment. I guess you would have to transform them somehow to get to in-phase and out-of-phase components. I'm not sure what to do about the irregular frequency spac…
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@dculp It turns out you can do frequency response by manually specifying the CCX cards. and interpreting time as frequency in the loads and solution. Here's an example.
