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Found 8 results

  1. Good evening everyone; I'm trying to figure out a way to analyse the temperature distribution across a brake disc using only the following loads: - An imposed rotation of 6000 rpm applied to the inner supports of the disc - An SPC constraint on the lower brake pads (as we can see in the image) - A Pressure load of 8,5 MPa applied to the upper brake pads (to represent the brake line pressure) So, basiclly, I want to understand how much heat is generated during a hard brake based on the contact friction alone; and how that heat is propagated throughout the disc without using thermal loads (unless they represent atmosferic temperature). Probably, the best option is to perform some sort of long displacement analysis (because of the rotation of the disc), but since there is heat generation involved I'm not sure this is the way to go. I would like to understand what type of analysis I must carry out, and how should I define the contacts between the disc and the pads in order to create an heat generation; Waiting for feedback; Thanks everyone! Luís Figueiredo
  2. 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??
  3. Sir, When we use the Autoprocess forming setups, for binder row, how is the use of the column 'Type'? When I toggle the option to 'Gap', the three columns as highlighted in the attached picture are available. Please elaborate how to fill those cells.
  4. Hello, I have been having issues with a model containing contacts and friction. The model is relatively straight forward, a multiple mast model with wearpads and contacts between pad faces and adjacent mast sections. When the contact is set to property type slide N2S, the analysis demands around 47GB for In-Core Solution. However when the type is set to static friction coeff = 0.15, the in-core demand becomes 80GB. The model on my pc then typically fails because MUMPS demands significantly more RAM. I've tried adjusting the search distance and using a PCONT card to define friction with little impact on MUMPS demand. Any suggestions? I currently have one PARAM card... PARAM,EXPERTNL,CNTSTB
  5. 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.
  6. 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
  7. 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
  8. Hello, Most of the commercial softwares use dynamic and static friction coefficients and the values are found in literatures. However Altair's Motion Sym, uses Lugre friction model and it is hard to find the correct values of that parameters because there is no information available such as what are the Lugre parameters of steel to steel contact or titanium to titanium etc. For example 1kg of block is modelled on a surface that has a F. coef of 0.3 it can start to move even with a small force pulling force applied although it should stay until prevailing of the friction force. Is there any way to handle Lugre parameters or is it a kind of bug?
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