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Found 52 results

  1. Hı, I want to create stress restriction in lattice optimization. So I am changing the value in the image below. But I do not see any change when I check the analysis results. (von mises). Can you help me?
  2. what is meant by all the stress options we get while analysis of 1d beam element for torsion. for example CBAR/CBEAM LONG. STRESS SAC
  3. Does anyone know how stresses are output in the material coordinate system?
  4. As far as I understand, the mises stress at the middle of the shell element is membrene stress, and the mises stress at the surface of the shell element is sum of the membrene stress and bending stress. and the hyperview can show the stress of the mid layer and both surface layer of the elements.(Z1, Z2, or Max) How can I show the contour plot of only the bending stress of the element ? I mean that I want to get the contour plot of value of ((Z1, Z2 or Max) - Mid layer ). Thanks for your help in advance.
  5. Hello, I am simulating a three point bending test for a composite laminate layup and I would like to find the force require for failure or alternatively a method of obtaining the point at which any specific ply has failed under the application of a specific force? Many thanks, Ahmed Gehad
  6. Hello I tried to optimize a modell with a lattice structure. This model needs to fullfill a certain stress constraint. The lattice structure is created, but the stress constraint did not implement properly. The full volume does it stick to the stress constraint, but the lattice structure itself does not and achieve too high stresses. What can be done, that the stress constraint is also taken account of the lattice structure. I aded following line to the .fem file: + LATTICE 1 0.1 0.7 10. I thank you in advance for your help!
  7. Hi all, I am trying to perform optimization in Radioss through -radopt command. The trouble is that computation terminates at the end of first outer loop when stress response is used: I have attached files, if anyone would like to check it out. test1_0000.rad test1_0001.rad test1.rad
  8. Greetings Forum Members, I am writing to understand the various result options (especially in stresses and strains) available in Optistruct (or any solver) Post-processing. Usually everyone follows the industry thumb rule of looking at VonMises stresses, Displacement (Mag) and Plastic Strain or equivalent plastic strain. But there are a lot of other result options available but many never seem to use it. I have attached screen shots of the some of the various result options (Stresses and Strains) available below:- Could anyone Kindly go through the above results options and explain the differences between them also establish a understanding of when to use them. For example, 1) what is the difference between VonMises, VonMises (Z1), VonMises (Z2), VonMises (mid). What does the Z1, Z2 and Mid imply? 2) what is the difference between P1 Major Z1, P1 Major Z2, P1 Major Mid and P1 Minor ? Even a simple answer in simplistic terms would suffice. Also kindly share any reference material available in understanding the results? What to look for after the analysis has been completed? Thank you. Best Regards, Bharat Pinapati
  9. Hello all, For stress analysis, I want to show the stress value of some nodes, in order to make a screenshot for documentation. To do this I put a note on the selected node, and in the note i write {entity.contour_val}. Now the problem is, that i get the value of the selected node and all of the nodes surrounding it. But i only want the stress value of that particular node. Does anyone know what to do? Thank you in advance.
  10. Hello, I'm trying to create a flexible body file by using Craig-Bampton Method. I need to write nodal stress values into the .h3d result file. From the global output request menu, I choose the stress option with corner location, then an ordinary analysis that has standard loadstep (for example linear static case) is run, and i can obtain the corner values. whereas, for the flexibody generation case, the nodal stress values are not written in the h3d file. Is there any way to obtain corner stress values in a .h3d result file for a flexible body generation?
  11. benf

    ERROR 320

    Hello, I'm trying to run a topology optimization on a 3D volume meshed with tetra elements. the objective is to minimize the Weighted Compliance. The responses I've chosen are : - weighted compliance - Vol Frac the constraints are : - VolFrac <0.1 - max stress < 870 MPa (via STRESS input in the DTPL card). I get the following error message: " *** ERROR # 320 *** Static load case 1 has prescribed displacements. The combination of global stress constraints and prescribed displacements is not meaningful. Optimization cannot be performed." I hardly see why it is not meaningful to use global stress constraints with SPCD... does anybody have a solution? Note: the SPCD is applied on a single node which is connected to the volume using a RBE2. Do I have to remove the area close to the RBE2 from the design volume?
  12. Hello, as suggested in another thread in this Forum, i tried the usage of dresp3-Card. What i want to do: - let excel calculate the tresca-stress (Input: max principle, min principle, output: stress (=difference between both input variables). - get the tresca stress back and use it for an "minmax-" or "min-objective" in optimisation What i wrote until today: LOADLIB DRESP3 GR01 tresca.xlsx $solid DRESP1 1 MAX_PR1 STRESS PSOLID SMAP DRESP1 1 MAX_PR3 STRESS PSOLID SMIP DRESP3 20 TRESCA GR01 MYFUNC 1 2 + DRESP1 1 2 + CELLIN C2 C3 + CELOUT D1 I also use a small excel-file, which calculates the difference beween "cell C2" and "cell C3" in "cell D1". Questions: - would it work like that ? (I can't test it at the moment) - What do I get with the DRESP1 / DRESP3 ? When using DRESP1 with "ELEM" and enter an element-ID, it would give ONE value to the excel-file, which seems to be pretty clear. But when I use PSOLID as the PTYPE, there might be hundrets or thousands of values (here: principal stresses). At that point I do not understand my own programmed code.. Maybe someone can help? I read the Tutorial OS-4095 and also a lot of manual pages. Thanks a lot
  13. Hi all, I want to compare the result of shell and solid element for a thin plate bending analysis. So I select a thin plate with dimension 100*100*2mm, the four edge of the plate are all clamped, and a uniform pressure is applied on the top surface. However, I got a different result from OptiStruct and Ansys with the same solid model. Both the material and the mesh are the same. The in-plane element size is 1.25*1.25mm, and there are two elements through its thickness. The maximum stress in X direction from OptiStruct and Ansys is 74.4MPa and 158.7MPa. It's so different. What's more, according to the theory, the maximum stress may be 154MPa, which makes me suspect the optistruct result. The maximum stress theory for four clamped thin plate under uniform pressure loading is given in following link http://www.roymech.co.uk/Useful_Tables/Mechanics/Plates.html What's the reason for this strange result? I have attached my HM file. In addition, is there any document which explain the different options meaning of stress result type and average method? See figure below Thank you Roy Shell_Solid.zip ShellSolidCompare.hm ShellSolidCompare.fem
  14. i'm an engineering student and I studied that the stress xx value in a plane 4 node element should vary linearly with the y coordinate and so should do the stress yy in the x direction, does anyone know how to see the stress gradient inside a single element? (e.g. with a control card or I don't know how) cause averaging method is nosense in this case since i want to know the values of stress inside that element without carying of what happen near to that element. thanks in advance.
  15. Hello, I am in need of help setting up an Optistruct run. I want to optimize wall thickness with a upper limit on stress. I have used a 2D automesh and I have a DTPL that veries wall thickness of the main body a base of 1.0mm to 10mm (defined by material property). I have the objective of the Optimization to Minimize VolFrac, and the responses set to VolFrac and StaticStress. Lastly I have set the upper bound of StaticStress to be the Failure stress with a OptimizationConstraint. Whenever I run the Optimization the wall thickness does not very with every iteration (stays at 1.0mm). Attached is my .hm model. Is there a tutorial that shows you how to do this? Thanks! V4SwingThic1.hm
  16. Hi, I have a solid cylinder and I need to get the stress results in cylindrical coordinate systems. I already defined a cylindrical coordinate system, but I don't know how to assign it to the elements. I appreciate if someone can help me with this problem. Thank you, Soraya
  17. Hi there, When defining the stress-strain curve for the material (/MAT36), should it be used the true curve or the engineering one? Thanks
  18. Hi all, I have recently started to learn solving with optistruct. While solving for a simple 2D shell static analysis of a plate with a hole under tensile stress, I noticed something strange. I applied tensile loads on opposite ends of the plate and did not apply any constraints at all. Optistruct solved it without errors. The displacements were obviously very large (10^9 range) owing to lack of constraints BUT the stresses were acurately calculated! Does anyone know how can optistruct recover stresses accurately with wrong displacement results?
  19. Hello everyone, Please see the attached images. The RADIOSS solver is giving; a strain in Y direction (unexpected) when the model is sheared in XZ direction a strain in X direction (unexpected) when the model is sheared in YZ direction Has anyone already faced such an issue? Do you have an idea what's happening here? Best regards, Sushant
  20. Hi All, I have set up a model of a pipe section and tried to subject it to torsion. The analysis completes but I have some unexpected results. I would expect the stress to be circumferential rather than axial. Have I set up the model incorrectly? https://www.dropbox.com/sh/rz0mgw3t1h91axq/AACnBNA5HjrX8AGIwFcpbQo3a?dl=0 Thank you Luke
  21. Hi Everyone, I am working with Radioss. I use TYPE 7 contact for this model. I wanted to check whether my model is working regarding with displacement or stress result for my BCs. But after analysis result it shows nothing every displacement result is zero and low Stress (Can see animation in this link https://drive.google.com/drive/folders/1jccvEqdd7xk5u3Zi_QyirAPrZYkpptGM). Before created this topic, I learnt RD-T3530 and RD-T3595. Can anyone take a look into my model whats wrong or what change I have to make. Thank you in advance. Animation : https://drive.google.com/drive/folders/1jccvEqdd7xk5u3Zi_QyirAPrZYkpptGM Regards, Salaya
  22. Hello, I have a double supported beam that I have divided into a non-design and design space. After running an optimization and generating the structure with ossremesh I did an FEA reanalysis on the model. When checking the stress contours I noticed that their were discontinuities between the design and non-design space. Running edge and face equivalence showed that there were no unconnected nodes. Both the design space and non-design space have the same material, but located in different properties. What could be the problem? Thank you, -Eric
  23. Hello, I have a question. Why in tutorial RD-3595: Three Point Bending the exercise expected results stress is upper than strength material. For example stress in solution is 1,203E+03 (Mpa) so it's 1203 MPa and the Rm (ultimate strength) Elasto-Plastic Material /MAT/LAW36: Inner, Outer and Flat is 400 MPa? thanks for answer
  24. Hi everyone, I am trying to model a helicopter blade, i have imported the CAD model.. etc until i created Plys. whenever i set the material type to orthotropic and hit update, at the bottom left it says "cannot compute material normal" and when i go back into the ply, the material type is back again to "all". would you be able to help me with this issue? Kind Regards, Mohamed
  25. Is it possible to calculate the Stiffness (N/m or N/mm) of the structure from any analysis??
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