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Found 133 results

  1. Good morning, I'm running a transient analysis of 2 gears (one of them with a preload and the other one with an imposed rotation). When I run it with Optistruct I get 2 problems: *** ERROR # 4965 *** Maximum number of time increment cutbacks reached, analysis aborted. The biggest problem comes here, if I analysis the results, the contact status is 0 everytime. The gears rotate but they don't seem to have a good contact. Moreover, I get high normal contact forces at points where there should be any contact (see image attached). I also attach the .fem to make it quicker and the .out from the previous simulation Thanks!! 1107rem.out 1207manana.fem
  2. Hi everybody Is there anyone here who has tried to model and run contact simulation using rough surface (see the picture ) ?? Cheers,
  3. Hi, I want to find the theory manual about interface type 24. Where is it? Thanks
  4. Hi everybody, There is someone here who has tried to implement (code) new contact laws in OptiStruct ? Best regards, Farouk M,
  5. Dear all I post for the first time. I'm Takky, Yokohama National University in Japan. Could you please tell me how to output the load force of side members and the barrier surface in contact analysis? I need its graph. I can't output the load force data of the barrier nor side member. I once used the output block on each RBODY of the barrier surface and side member, but no data was output. On HyperGraph, only "Global Valuables" is available, but no other data in "T01-file". In this analysis, the bumper model crash into the rigid offset barrier surface in front, in initial velocity of 50km/h(13.9mm/s). The analysis sample on this image, I wanted to output the each load force of right and left member, but couldn't. In another analysis, I made one rigid body from two members and tried as equal, but couldn't. So, it's not because there are two rigid bodies in rear of bumper, I think. I sent its HM data together. Any ideas?? bumperA_inivel_2.zip
  6. Dear All, how can i resolve it. im having all solid elements in my model. gap between two part is 0.2mm friction is 0.05 what additional parameters i need to choose in type 24. i'm doing failure analysis with JC material model regards, Ganesh m
  7. Datta1234


    Hi, I am trying to simulate contact for performing frontal crash analysis of a chassis having a tank. I have a tank which is wrapped by two brackets and supported by rubber. This bracket is welded to a chassis. I need to create contact for the following- 1) Between tank and bracket. 2) Between rubber and bracket. 3) Between rubber and tank. It is attached to chassis as follows- I know that I need to create Interface. Please tell me for each case which Type interface should be used and which should be selected as master and slave? Thank you, Datta
  8. Hello, I would like to have your expert opinion in one of the problems I am currently working on. Part of the simplified geometry is shown in the attached picture. As seen I have two cylindrical parts in contact with an interference fit of 0.001 inches. In addition to that a pin is installed and goes through (with a size to size connection) both cylindrical parts. I decided to perform a quasi static non-linear analysis, firstly by solving the interference fit and pin connection load case and then continuing with the load on the structure as a second load case. When I solved the press fit problem (without the pins), I had no problems, both the displacements and the stresses looked reasonable. But when the pins are included into the solution I am having a band of peak stresses (well beyond the material's yield point) where the pin contacts both cylinders (see red oval in the attached pic). This happened with almost every type of contact connection I tried between the pins and the cylinders (freeze, slide, friction etc). Same results when I replaced the 3D pins with 1D elements with RBE2 connections (to connect them with the cylinders). One solution is to ignore the pins and continue with my solution and then perform a detail stress analysis of the pins based on my results, but before doing so, I would like to know that I have tried all possible scenarios with the pins' contact. Any suggestions? Thank you in advance. pin.bmp
  9. Hello there, basically I am doing an analysis of our brake disc for formula student in radioss. So far the structual part works and the energies look fine. The next step is to get the thermals in there. In the documentation for the type7 interface there exist an Fheat. But I can't find it in Hypermesh. So my Question is whether the enegry transformation into heat is working or not if only I_the is activated. Another strange problem I am facing at the moment is that if i define a starting temperature in Ti and T0 (~300 K) the results still show me 0 K. By the way I am using Block 120 because on the cluster only 120 is installed. Looking forward for some help.
  10. Hello everyone! I need your help. Fllowing picture shows the case i want to simulate. I have a problem to create the contact between the component and rigid walls. Walls have to be fixed and the part lies on them and is fixed by screws. I would be very happy if i get your help. Many Thanks in advance! Best wishes from Germany!
  11. Hi all, In my model, there are many contacts. From the result, I found the contact energy was large. How can I find which contact makes the large contact energy? In LS-DYNA, each contact energy can be output separately. However, in Radioss, it seems that we can only output total contact energy through global variables. Best Wishes Roy
  12. Two bodies are connected by means of bearing (upper race and lower race bolted to respective bodies). Detailed analysis (ignore bearing model) is not required. What type of connections could be given between two components? Can we assume a block instead of bearing, and give what type of connections?
  13. Hey, I try to simulate a large displacement movement and have a problem. I got two simulations and want to evaluate the SPC-Forces, which are completely different, although the model is the same. The constraint is placed in the middle of the green component and connected to it, with rigids (see Figure). In the first simulation, the total displacement of the green component is 350mm (due to constraint) in x-direction. In the second simulation the total displacement is 50mm. When I evaluate the force-displacement plots and compare them, the results are completely different, which makes no sense. For example, in the first model the force at 50mm displacement is 6,7e+05 N. But for the second model, the force at 50mm is only 8,19e+04 N. But they should be totally the same to my opinion. Somebody any hints? Greets Elvis
  14. Hi all, I want to set up contact between two bodies in optistruct for modal and frequency response analysis, but I don't know how to do it? Is there any example for reference the detail process? Thank you Best Wishes Roy
  15. I am trying to simulate an autofrettage process with the optistruct solver but i am not able to get any plausible results. In theory the process and simulation should be quite easy. We have two parts: a swage and a tube. The swage (which has a slightly bigger outer diameter than the tube) is pressed through the tube which results into contact with friction and plastic deformation in the tube. I meshed both the swage and the tube (only one quarter of each and conditions for symmetry to reduce the calculation time), defined all the boundary conditions like constraints and the load (forced displacement of the swage) but somehow the contact condition doesn't work at all. I read several tutorials and have tried different combinations of contact-surfaces or set-entities which were linked by a contact interface. I tried the preset contact types like slide/freeze/stick as well as a contact property with MU1/MU2 coefficients. When I use slide or freeze (images below) I get extremely high deformations and it looks like the points where the first contact occurs don't separate anymore, In addition to that I don't understand how they can already be in contact at that point since the contact should occur later when the bigger diameter hits the edge of the tube. Displacement scale factor is always set to 1.0. When I use the contact property (pcont) the calculation takes forever and I don't get any results (no convergence). I already tried to increase the number of iterations up to 50 and NINC up to 25. I would really appreciate any helpful advice or maybe someone with experience could check my model file. test_12.hm
  16. Hi guys, Lets say I have a design space modeled as a geometry file. I have a set of cylinders modeled as 1D Beam Elements which should all lie within the design space box. The idea is to use a contact adjustment calculation (=contact initializatio) between the cylinders and the design space. I tried to model it with a two contact surfaces but the elements (1D) are not valid.... is this even possible to do with Hypermesh? I wrote the problem with illustrations into the attached .pdf file. Any help is greatly appreciated! Thanks! Merula contactProblem.hm ContactProblem.pdf contactProblem1D.hm
  17. Hi, I've started to use Radioss few days ago, and I'm performing an impact analysis on a vehicle component. Actually I'm not able to find the Autocontact tool (as in Hypermesh Optistruct) in order to set all the contact surfaces. Can you tell me where could I find it please? Thanks in advance
  18. Hey! I am trying to perform a structural and transient analysis on a Roller Element Bearing model. I am able to perform simple static analysis but I would like to utilize Hyperworks to simulate the following conditions: Inner race to be rotating with a constant velocity and a fixed radial load is applied. Outer race is fixed. The balls should also be rotating. I wish to know: 1. How I can give a constant velocity to the inner race of the bearing while also allowing the balls to rotate? Which card am I supposed to use? 2. What kind of contact constraint should I apply. Right now I am working with slide contact only. 3. Is quasi static analysis adviced or implicit non linear? There is one video but in a different solver which does what I have been trying to do. I wish to do it in Hyperworks. Here is the link: Also please suggest whether optistruct's non linear can be used or whether I should switch over to a different solver module! Cheers
  19. Dear All, can you please help me with, How to apply enforced displacement on shaft and fixed constraints on hub as shown in figure. i'm confused in load collectors, where to assign spc and where to assign spcd and in which collector. also want to know about search distance option what it means actually. is it a gap between contacting bodies? regards, Ganesh
  20. 3D model with solid elements, there are two surfaces in contact and friction interaction were set in Hypermesh. When .inp file was imported to ABAQUS and check data, there is a warning "the slave assembly has 1200 nodes in common with master surface". Should I separate the nodes on the interface and how to do it?
  21. Hello, Since the contact surface is deformed in the current analyses, I would like to use tracking system to obtain the projection of the contact forces on the element surfaces. I could manage to use tracking system for displacement but I could not find a way to use for vectors of contact forces. the toggle A picture of the issue I mentioned, is attached to this message. The swicthed that is written "use tracking system" cannot be activated as shown in the second picture, Thank you for your help in advance.
  22. Oli


    Hello, I want to simulate a rivet Joint just applied shear force. Between the rivet and the hole in the metal Sheets is a gap. I get convergence but the rivet turns a Little. u can see it if u watch the displacement Contour plot on the rivet which is not symmetric. Is that because of the coarse mesh? I tried to use gap elements but maybe i put some wrong Setting. attachted are the model. Can anybody help me to fix the Problem? rivet_joint.zip
  23. Hi Everybody, I would like to model a Contact-Friction anlayse between two bodies with a pressure load and relative velocity in two time steps. At first time and second time step I would like to apply a pressure At the second time step I would like to apply Relative movement ( with the presure along with friction applied)between two bodies. Please help me in this regard! Thanking You, Fares
  24. Hi, I have a problem with contact analysis. My model is working fine in one direction (let's forget about the connection between the bearing and the gearbox), i.e. the bearing pushes away the flange. However, if I change the direction of the force, in which case the bearing should slip out and has no effect on anything, the bearing still pulls the flange. What do I have to modify to make the bearing available to push the flange but not pull? Thank you aecyd bolted_flange.zip
  25. Hello! I've started using hyperworks a couple of months ago for my research and I still don't really know my way around as I have no previous experience in simulation software. I would like to do a contact analysis by putting two thin foam films (about 0.2mm) on top of each other and see how the impact distribution is different when I change the young modulus value for the top or bottom films. 1. Can anyone advice on which radioss (bulk or block?) I should be using? 2. Shell or solid? 3. And is there any similar tutorial that would be useful? I found "RD-2100:NLSTAT Analysis of Solid Blocks in Contact" but I'm not sure if it's appropriate for the analysis I am doing. What is NLSTAT by the way? 4. Any other related advice would be greatly appreciated as well.
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