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Victor
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Since it's a linear analysis, rotation angles have to be small. Under this small angle assumption, rotation of a mesh is really a linear translation of each node in the direction tangent to its circular path. If the angle is bigger, then the transla…
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Oh, I see that mode now. Surprisingly very low compared to the unconstrained one! Makes sense now since it's dominantly a flywheel mode compared to the higher one being mostly a shaft-only mode.
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Don't use constraint equations. Those will artificially stiffen the element adjacent to the axis. Just use the X-displacement constraint on the axis. That also constrains rotation about Z. This way, for the model you sent, there's no need to adjust …
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I don't have an intuition for the magnitude of those high frequency torques. I tried refining the mesh but it didn't change it. I suppose that's just how it is. If you look at longitudinal stress, and turn on the animation, you can see the shaft twi…
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That vibration will be higher frequency modes above the fundamental natural frequency. The sharp edge of a pulse contains high frequency components that will activate them. You can change the analysis type to Modal vibration with about 10 modes to …
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There's no simple way to do backlash. I expect you could use a compression-only or tension-only material, which CCX has. You'll have to enter the definition manually. It's a nonlinear problem so at least you'll need to use the CCX solver with nonlin…
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Mecway doesn't have an API but you can edit the .liml file with a text editor or batch text or XML editing tools. Search for the numerical value of the force you want to change. I don't know about the hyperelastic question. I hope someone like Serg…
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Constraining the on-axis edge in the X direction like you have done also constrains it against rotation. So it's already OK and there's no need for any extra constraints. If you refine the mesh, you'll see that boundary's displacement looks more re…
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1) Yes, you can add more rotational inertias as separate loads. It just doesn't allow a single one to be spread over more than one node. 2) Yes, you can couple torsion between, say, nodes 1 and 4 with a constraint equation like 0 = 1 rx4 + -1 rx1, …
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Yes, trial and error. A reasonable starting value is young's modulus divided by a characteristic thickness, such as the thickness of an element. Or you can imagine there's a thin layer of extra material between the two parts, and use the thickness o…
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In principle, yes - they have the same physical meaning. Here are some differences: * Elastic support requires you to tune the stiffness parameter to be high enough that it's almost rigid and low enough that the solver doesn't fail. * Elastic …
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Probably not, at least not for a while because of other priorities. Also, that would only be if Netgen (the "internal" mesher) is already available multithreaded.
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One end doesn't deflect much because the 4 lower suspension arms at that end aren't set at truss. Note that this is a 3-state checkbox. If you have more than one element selected and they don't all have the same setting for truss, it'll show an ind…
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I don't think so. You could check Task Manager to see if CPU utilization is more than 1/number of cores.
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The heat flux is already given in the solution and it doesn't have a single value for a surface. Do you mean average heat flux? Or heat flow rate, with units of power? In the latter case, you need to integrate the heat flux X values. There's current…
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Nothing specially for that, but some ideas: If it's a straight line, In wireframe view, you could rotate the line so it's normal to the screen and select them with a rectangle around the end. There's also the cutting plane to hide foreground or ba…
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The "flexible joint on beam" is for this type of joint - not only in the middle of a beam. But it's currently only for the internal solver. I'm not sure how to do that with CCX. You might need to model the two beams separately (no shared node) and …
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You can use beams with the CCX solver and nonlinear but not the internal nonlinear one. In case you need circular tubes instead of rectangular section, they have to be line3 elements. Use Mesh tools -> Change element shape to change them.
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And the property names: Geometric "thickness" "ca" "cb" "cc" "cd" "ta" "tb" "tc" "td" "la" "lb" "lc" "ia" "ib" "ic" "id" "recta" "rectb" "rectthickness" "roundod" "roundid" "iyy" "izz" "torsionconst…
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Here they are Material types Geometric "Plate" "C" "T" "L" "I" "RectBar" "RectTube" "CircularBar" "UniformCircularTube" "UniformGeneralSection" Mechanical "Isotropic" "Orthotropic" "StiffnessMatrix" "AnisotropicPlate…
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Noted. Actually I didn't even know ZZS improved stress existed.
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I agree that not averaging them would be more accurate. With the constraint of node values being points on a single-valued function, averaging seems like the best it can do. In future, I might have to add a new kind of mixed field variable type that…
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I think I understand now. Sum of applied forces? Not currently. I think you'd have to solve it then use the table to select the loaded face and element selections and copy them to a spreadsheet to sum. Or maybe use CGX for that.
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Can you clarify what you mean about separating the integral for node and acceleration forces? Do you mean the "reactions" due to inertia in a dynamic analysis? I'm not sure if there's enough data in the .frd file to identify which is which, if it in…
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DaveStupple, adding commands there just add them to the existing *STEP section. Define the displacement constraints in Mecway, then make a new *STEP section that has forces and no non-homogeneous displacements. Here's how to define a 2nd *STEP sec…
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You can use element or face selections instead. Node selections is risky because for shells and beams it would depend on CCX always generating new nodes using the same numbering scheme. It'll also have to detect and cope with manually added OUTPUT…
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Probably not. You can copy and paste from Mecway's table into Excel. How did you make your graph?
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It's because the time steps only go up to 0.45 s but my formula has 4.5 mm displacement at 0.5 s.
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I agree with your assessment that the force isn't resisted so the o-ring flies away. Friction might be difficult because it has to be high enough that it resists the applied force at every time step, especially during the transition from deformation…
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The main purpose of this item is to activate thermal stress so it's called that. It also happens to have one parameter which is the reference temperature. Though I can see that it also makes sense to think of it as being just the reference temperatu…
