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Victor
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Comments
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OK no problem.
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I'm not sure if I understand you, but it sounds like you want to prevent them from deforming, so they act as a rigid body? A simple way is to set a very high Young's modulus. If you only want to constrain their joint to 90 degrees but still allow …
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The cutting plane has been in all versions and is the slider at the top-right of the toolbars. Slide it half way to hide the front half of the mesh.
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From these pictures, the negative values only seem to be patches in the middles of elements, so it looks like just the interpolation used by the display and you can ignore it. The node value look to be all non-negative. The existence of patches co…
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The values at the nodes should always be nonnegative. A common way nonphysical results like these can appear is through the interpolation for finding values between nodes. It uses the elements' shape functions to interpolate the colors on the displa…
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Yes and yes.
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Two main approaches: A) Use a reference frame rotating with the blade. Linear dynamic analysis is probably sufficient since there are unlikely to be any large displacements. It depends how much rotational vibration the shaft has because angu…
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That can be a bit of a problem. You should be able to work around it by setting a larger number of time steps and a corresponding smaller time step size. Then the automatic time stepping should bring that back to a sensible size as it solves. The nu…
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1) Set the environment variable OMP_NUM_THREADS = 8, where 8 is the number of threads you want. It might be best to make that a bit less than the actual number of cores, but I'm not sure. This PC -> Properties -> Advanced system settings ->…
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I used trial and error until it damped the oscillation for most of the time steps. There isn't really a proper value since it doesn't represent a real damping effect. It's only valid if none of the time-dependent loading (ie. accelerations) have any…
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On second thought, please don't publish a user.config from Mecway on the internet because if you're a paid customer, it contains your product key which is private. Perhaps send this through email instead.
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I would think any dynamic analysis could be used as inertia relief, even if it's inefficient on computer resources. Either use a single time step or have damping so the final state is a rigid body acceleration with deformation from the loads. Note…
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Sorry about the late reply. The oscillation is because the initial condition is the undeformed state, so it falls down under gravity, then bounces back and oscillates. Mecway doesn't currently allow non-zero initial conditions so you might have to u…
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1. Yes except with the Tsai-Wu criterion instead of von Mises.2. Yes 3. Yes except it only checks the top and bottom of each layer, not anywhere in between.
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Not quite a tutorial, but here's a quick example of the Tsai-Wu failure criterion: Make a model with shell elements and a laminate material. Enter the parameters in Material Properties ->Failure criteria -> Tsai-Wu Solve and see the result…
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That's a very nice tutorial but I think it's too dated to be much use for Mecway. It doesn't seem to have examples of the different-materials-on-each-layer type of laminate material which is the only one that Mecway and LISA have now. There's an…
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Self weight isn't automatic so yes, you have to specify -9.81m/s^2 gravity.
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It looks like SAP's two formulas might be equivalent (I haven't checked) and the latter is the one it actually uses but the former, with the integral, is more intuitive as a definition.
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Not directly but two ways around it: if you have base excitation of a rigid base, then you can use a fixed base with gravity load on the whole structure as acceleration. You can copy and paste tables of time-acceleration data into that. You coul…
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I'll look into adding the membrane forces. For out-of-plane shear forces, LISA's results often had quite large errors so I removed them from Mecway. I'm not sure what was wrong with them. The attachments show the kind of errors to expect. The plat…
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Please attach the user.config. Maybe it's not correct.
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Just curious what makes this problem challenging. Is it hard for solvers to converge? Or something complicated about the boundary conditions or the load changes while it's deforming?
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It depends on your goal. If you want to find the stress in or right next to the weld, ideally model the plates and the bead itself using solid elements in a single mesh. You can also use bonded contact to join the weld bead onto the plates but it …
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After you use a unit in a model, it should remember what you prefer for other values with the same quantity. You can also create a starting model that has a dummy material with the units you want. Then if you build a new model off that, new material…
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No, you shouldn't need both. The thickness in the material properties is for shell elements and is ignored for solid elements. There, you would define thickness only by the geometry (node positions).
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Yes, the animation briefly stopping when you move the mouse over the graphics area is normal. It's also a bug and I'll try to fix it for the next version. Thanks for pointing it out.
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It doesn't currently keep the node selections because any shell or beam elements will cause them to be renumbered when they're expanded in the solution and that's a little harder to keep track of. You should be able to work around it by making an el…
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Mecway doesn't have a tool to fill in holes with mesh. If you just select the nodes on the edges, then the Merge nearby nodes tool will only affect those nodes.
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Mecway doesn't have a way to define node coordinate systems other than defining *TRANSFORM by hand. Is your aim to get a plot of the radial component of displacement instead of the X,Y,Z components? This sounds like something that would best be done…
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You can highlight free edges with Tools -> Labs -> Find non-manifold shells. If the Labs menu isn't visible, turn it on through Tools -> Options -> General -> Labs. I'd like to make this into a proper feature eventually. JRP, can I …
