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Found 111 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. 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
  3. Hello I am using RADIOSS to simulate a crash test which I have previously done. The trajectory of the impactor before impact is complex and requires several linkages and mechanisms to set up. The area of interest is the post-impact behaviour (stress/strain) on the target component, as well as the trajectory of the impactor. When I run the impactor by itself, to see the launch trajectory, I get a reasonable run time of about an hour. When I run the impactor with a simplified initial velocity + the target with all the contact and failure cards defined, I get a reasonable run of about 3 hours. When I run the full model: impactor with the initial trajectory + the target with all the contact and failure cards defined, I get a run around 12 hours to reach the impact, and another 12-24 hours to get results from post impact trajectory. I believe this is partly due the finer mesh required for the target model. I was hoping there is a way I can split the analysis in two, using the results from a the first as an initial condition for the second. Consider the following scenario: Model A: Simple model with only what is required to set off the trajectory of the impactor. The target is not modeled. Run from T=0 to T=T_impact. The run is stopped at the moment where the impact would have occurred. Model B: The target, with finer mesh and contact and fail definition is introduced, and the analysis is "RESTART" picking up from where Model A left off. In other words the target (with finer mesh) only appears just before impact onwards. This should theoretically cut down the majority of the analysis time. Is there a way to set up a RESTART file with introduction of new elements / properties / fail cards, and linking it to a "Stopped" run? I hope the diagrams attached illustrates what I'd like to do. Please let me know if there is a way to do this. Thank you. Best Regards, MN
  4. Hi, I have two main questions (for now) 1) I have define an advance joints between two bodies and is there a way to define the contact force between these two bodies without using the 3D or 2D contact simulation? 2) what does it mean when i define output-force-body and how can i see the result in hypergraph or hyperview? thanks for the help!
  5. Hello, I want to simulate the following mechanism I need the orange pin to slide trhough the green slot when the green slot moves due to other machanism movement. This is the configuration of contact that I used: Nodes on the all arround the slot are the slave and all of the pin elements (membrane of a 3D) is the master. And the results are these: what do you suggest i can do? What is wrong with my contact card, or what other approach do you suggest? thank you for your itme.
  6. Hi, What's the difference between the contact properties (Normal force) in Motionview. i have tested Impact and Volume model and the contact force between the two are different. Which should i take/use for the Simulation. thanks in advance.
  7. Hi, I am trying to launch an optimization on Inspire but I am always getting this error about unrealized contact: # -------------------- Progress Tracker -------------------- hwfdmfeprocessor process id = 15200 # Opening Model # Model opened successfully Client = Inspire 18.3 10526 Name = ADCS_V9_Config5_Tests7_2 Maximiser la raideur Masse 25% Fmin 100 Hz (9) ModelName = Model stmodOffsetId = 2 # RunType: OPTIRUN_ANALYSIS = 1, OPTIRUN_TOPOLOGY = 2, OPTIRUN_TOPOGRAPHY = 4, OPTIRUN_SHAPE = 8, OPTIRUN_GAUGE = 16, OSSMOOTH_REANALYSIS = 128 RunType = 2 # Using CAE_HOME='C:/Program Files/Altair/2018/sTInspire2018.3/hwx/bin/win64/' # Time 17:17:59 RUN_STATE = 1 ## Run started # Time elapsed - '6' Seconds <==> Total time taken - '6' Seconds RUN_STATE = 3 ## Generating fresh mesh/Using old mesh #--------Generating fresh Mesh RUN_STATE = 7 ## Meshing completed successfully # Time elapsed - '1511' Seconds <==> Total time taken - '1517' Seconds RUN_STATE = 15 ## Realizing model #--------Unable to realize contact (Contact 50) as UdbSet for Primary features can not be created #--------Unable to realize RUN_STATE = 527 ## Synthesis run completed successfully # Time elapsed - '68' Seconds <==> Total time taken - '1585' Seconds # Error - Unable to ralize synthesis data RUN_STATE = 1551 ## Done # Time elapsed - '1' Seconds <==> Total time taken - '1586' Seconds # --------------------- END ----------------------- Could anyone explain me what the problem might be ? Because in my model the contacts seem ok (those are default contacts obtained after using boolean substractions of non-design spaces on a design space volume to avoid intersecting parts) Thank you in advance,
  8. hi, i have created a 2 3d rigid to rigid contact, but when i try to run the calculation, this message log Shows for the two contacts. i have checked the model in Hypermesh, there is no free edges or red line in the so called model or geometry.
  9. Dear All, I'm using HM as a pre-processor and optistuct as a solver. want to simulate following condition shaft of size =10.000 mm and housing = 9.999 mm(interference of 1 micron) when i'm trying to rotate shaft using motor by keeping fixed housing. 150 degree temp is generated. want to observe the effect of temp on contact pressure and deformation of housing ID and Shaft OD. model is setup is done as per NLQS. what extra i need to incorporate to observe above effect regards, Ganesh
  10. Hi, I've a problem with my 3PB model of a sandwich structure (honeycomb core). Contact between sandwich structure and supports isn't realistic. I set contact in "SLIDE" but the result is wrong. So I obtained a displacement of 177 mm with a force of about 15000N, not real. I can't also view the results of CFAILURE, but I've set it in output requests. Can you take a look to my model? Thanks in advance. Hearing from you. Regards. 3PB_1.hm
  11. 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
  12. Hi. I want to be compare the composite analysis and contact surface (freeze) the example is above picture. And I want to check the ERP between 0~3000Hz. and I can get the follow this. (damping material density is 1856.07kg/m^3) The blue line is contact surface(freeze) model, The black line is composite model. why the blue line is more big value than black line abouy twice. why the blue line is more big value than black line. I want to know why two lines are different exactly. contact_al_dam.fem contact_al_dam.pch compostie_test_revised.fem compostie_test_revised.pch
  13. Hi Guys, Im doing frontal collision using radioss, spot weld and adhesives were provided using connectors. Since there were interferences between spot weld and adhesives as shown in the figure. Both spot and adhesives will be there in model, is it advisable to continue with this. Since my major interferences and penetrations is between spot and adhesives. Can you provide me a better solution. Also while providing type7 contact, Case1 In my model both shell and solid part persists i have directly selected those parts in Master Entity and Case2 In my model , i have created skin for all solid parts with a thickness of 0.01mm and updated those in Master entity along with shell parts in this which one is advisable, how to establish contact for those solid components.
  14. 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
  15. Dear All, @Prakash Pagadala in attached image green- housing yellow - shaft blue- ball ball makes a contact with shaft at 2 points and with housing at 2 points. at every contact there is an interference of 3 microns. housing is fixed and shaft is allowed to translate axially. i tried contact with static coefficient of friction and and clearance value but still groove surface of shaft and housing is penetrating the ball and vice versa. can anyone suggest how can i work on this??
  16. I have components in the assembly and i want to find the IDs of surfaces which are really close or almost touching other component. Is there any way to find out those details?
  17. Hi all, I was running a model in Optistruct 13.0 dealing with a two step non linear quasi-static analysis of two plates coming into contact. In the first step my goal is to make sure the two plates don't come into contact; let's say my initial gap is 5 mm, one plate is pushed down by a force of 100 N, the other one is fixed at the base. At the end of this step the two plates should have minimum gap between them, in other words no load should be transferred from one to another. After the second step in which I apply a force of 1000 N, the two plates obviously come into contact, resulting in a load transfer to the spcf applied at the base of the fixed plate, since friction between the plates is activated. I tried using a gap element in order to simulate the problem but no matter how I change the values into the pgap card (for example I first put a value of Kb equal to 25 N/mm to make sure the pushed plate didn't reach 5 mm of displacement with a force of 100 N.... didn't work, then I put it equal to 0 and I obtained the same result ), at the end of the first step the gap of 5 mm is always reached, resulting in load transfer. How can I avoid this situation in order to make it work properly? I'll attach the .hm file so you can check it. Thanks for any replies, hope someone will help me with this matter! model_with_gap.hm
  18. Model description: A set of gears Load:Torque Non-linear analysis conditions (NLSTAT) There have contact between the gears (Slide) Problem Description: The ideal result should be that the largest stress is at the root of the tooth, but the analysis result is that the largest stress is at one point of the tooth surface. This maybe stress concentration. Is it a model problem? Or, if not, how to solve the stress concentration problem caused by this analysis. When I look at the results at different times, stress is still relatively uniform even at t=0.9, but stress concentration occurs at t=1.0. Is the load equally divided? The following pictures show the stress results On the left is t=0.9. On the right is t=1.0.
  19. 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?
  20. Hi everybody, I was running a test with optistruct using two simple cubes. They are both fixed at opposite ends. Their faces are separated by 0.1 mm and can, if pushed, become engaged in a contact (type SLIDE). Type of analysis: nonlinear quasistatic. Issue: Even if I fixed both cubes at their bases and there is no applied force and no contact is engaged (shcdist=0.001 and the solver warns me that no contact elements have been defined during the analysis), the cubes translate of 2 mm as if they are moving like rigid bodies. I have already tried to constrain some more nodes, to no avail. Any explanation for this thing by anyone? Thank you in advance. Find attached my .fem file to check SHRCTOL001.fem
  21. Hi all, 1、For a problem with large deformation, the contact status between two objects will change. Some location will come into contact while some other location will separate. What's more, relative sliding may also exist. How to choose the proper parameter values in contact property card for this problem? 2、If a linear static analysis is chosen, could the contact status change during deformation process? Roy
  22. Hello, I would like to do some lattice optimization in Hypermesh. However, I need to know if it is possible to have a different mesh size for the lattice sections compared to the solid sections. The way I understand lattice optimization in Altair is that the element size you mesh with originally will determine the average length of the lattice struts. For example; I tetra mesh my model with a size of 2, the lattice beams have an average length of 2. However, I would like to have a mesh size of 0.5 with lattice elements of length 2 (or vice versa). My game plan is to run a minimize compliance with volume fraction on my model with a penalization of 1.8 (low porosity). Then use the results of the compliance optimization to split my part into sections for a given element density threshold. I should end up with solids for the lattice elements and solids for the non-lattice elements. The lattice solid sections will then be filled with lattice beam elements from another lattice topology optimization. I want to remesh each solid individually for different lattice strut sizes and types. Contact surfaces will then be used to connect the solids together and then run the Lattice optimization. The end goal is to use mesh refinement on the non lattice sections to check the validity of my model as well as experiment with different lattice sizes. Any advice is greatly appreciated. -Eric
  23. For Modal and Stiffness(torsional and bending) of ladder frame chassis, is there any significant difference in results when I use stick contact between frame and cross-members or when I use shell/rigid weld elements to connect cross-members and long members?
  24. Dear Sir, I want to do a three point bending test of carbon fiber laminate in Hypermesh with Radioss. I found something puzzle when i create the contact between components after i had defined materials, properties (CFK using M25_COMPSH and property with it using P17_STACK), plies, laminate and some of boundary conditions. I chose TYPE 7 as the card image to let laminate be a slave entity and impactor be a mater entity but i found i cannot select my laminate component in the option(i can only see other component) Is there any mistake in my operation? Here are some pics under. I am exactly green hand in radioss, my apology... and I hope someone can help me on this.
  25. 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.
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