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Sergio
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Even if CCX solver has a specific PRELOAD card suited for this purposes, I'm still using the classical approach of adding thermal expansion coefficient to the bolt material and then apply a low temperature boundary condition to the bolt nodes to cre…
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You could fix (3 dof) all nodes of the body, or use the RIGID BODY card in case of using CCX solver.
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@Victor, have been working in another complex skid this week, and I decide to don´t delete (and not use for any component) the default one. Guess that was a good move as in this way I know exactly where new elements will be created (on the visible d…
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I also like the idea, big software companies has implanted the idea that engineering can be done only with insannely expensive software tools, and for most of the cases can be done with free or affordable ones. My best wishes.
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It takes less than one minute in a Xeon with 18 cores and 32 GB of ram (and ssd disk), maybe two on an old laptop with i5 and 6gb. In the Xeon I have a good Quadro vídeo card, but even that it cannot show the result plot at maximun resolution setted…
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Maybe related, can the de center of gravity computed also once the densities are defined??
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Hi, you can select all the nodes and then apply a cero displacement (three directions), to get all the elements fixed. But why you need to fix it all? Regards
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Now my question to the experienced people of the forum...If I would has to analyze a chasis very like this one, with the objetives of the analysis being max displacement, stress (under steady load and lifting operations) and probably eigen modes ht…
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I have made a quick analysis, the only issue is that you cannot use the Mecway internal solver as the mesh has triangle elements. Anyway CCX has solved without problems.
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Hi Sebastien, this is your part meshed in Salome, the first pictures is meshed as it (element are unconnected at face's unions), and the second one is with a little of geometry treatment to get the full connected mesh
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Can be the different sides of the shells elements painted in different colors to easy identification?
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How does work the multiple delete in the model tree? Is only the new "Delete all" entry in the menu or is possible to select using ctrl and shift?
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Have worked with parts that suffer a lot of deformation/stress due to thermal shrinkage, what we did for that parts was model the geometry in "hot state", and then add a thermal step to the simulation to decrease the temperature and shrink the part …
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Congrats Victor, those are really usefull features! Is there a way that the mehs of the first part (from imported geometry) goes directly on the default component?
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A little late, but here are the results, hope they be usefull. In the PDF file are the load deflection curves and stiffness values for each direction, assuming a preload of half of the maximun load (8mm) Regards
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You should remove the card NODE FILE and EL FILE writted by Mecway (using the "don't generate keyword" option on the CCX branch) and then write your own ("Custom step content") using the option OUTPUT=2D in the NODE FILE and EL FILE cards to avoid t…
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Can you measure the unloaded height of the mount? I'm not sure if the height on the table is with or without preload.
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There is very few info on the site! It should gave you at least the static stiffness in X Y and Z direction. I would start defining a spring by two nodes separated by the issolator unloaded height, so when you apply the load (weight) you would hav…
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As far as I understand probably your mounts performs lineal at least in the range of your application, so then if you have the stiffnes vales for each direction you can use three SPRING elements directly. I worked with automotive engine mounts that …
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You could use SPRINGA elements to reproduce the behavieour of your rubber mount assy. As far as I understood from de CCX documentation you can enter the force/deformation table to represent your non lineal mount assembly. I'm not sure if one element…
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I have done the mesh in Salome. Just explode all the surfaces, then join again to make the mesh coincident at the intersections. There was one horizontal surface that was not exploded, so I divide it using the vertical ones.
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This the model meshed with coincidents nodes in Salome, now I would like to see the results!
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As is a relatively simple geometry, I would work with a solid mesh. I'm not sure how must be treated the unions between two crossing surfaces using shells. Anyway, as Disla says, with Salome you can join the surfaces and create a mesh with coincide…
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Another trick is to add an extra point at very large strain (100% strain and compute the stress for this point to keep the tangent modulus constant) in order to help to converge in case of having a very small high plastic strain hot spot in your mod…
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Hamwik, those are engineering stress/strain values, you must transform to true stress/strain to use in CCX (true stress is a little higher than engineering stress). Also, the second point of your PLASTIC card is the ultimate stress/strain, but you m…
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Sounds similar to NX "load cases". In that, you first define several loads and bc, and then create a load case dragging each bc and load to that. In that way you can create several load cases (the can even be different kind of analysis if I remember…
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I don't understand your question, if you apply the load in the center of the flange, then will appear some flexion and moments on the bolts as is not in the same direction.
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Bolt has no preload and the union start to gap?
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Is there any standard dimensions for preloading the bolt by displacement? I always preload up to 75-85% of material yield, mostly using the thermal procedure on a middle portion of the bolt flank. Normal torque procedure always remark that with n to…
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Nice work! What is the "stress_tt" variable?
