https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/Testingen-USTelligent Community 13https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74703/adams-hardware-benchmarking/1434932Thu, 01 Oct 2026 00:17:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:9f3b8850-a856-4dd1-b9fd-28f5bc713f0eRishikesh MokashiHi Harish, I see that you are already in contact with our team on this. Please feel free to contact us by sending an email and we can assist further. Regards, Rishihttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74703/adams-hardware-benchmarking/1434930Wed, 30 Sep 2026 15:33:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:d8daa5e8-6441-449a-8af7-e370005b2112MC202509189142Post moved from How to use the communityhttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74703/adams-hardware-benchmarkingTue, 29 Sep 2026 23:41:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:008ca277-1193-40bf-b1b3-8b58fccc955bHarish SonawaneAre there any benchmarking data or guidelines showing how ADAMS solver performance scales with CPU clock frequency, core count, FLOPS, L3 cache size, and RAM speed?Adamshttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/Tue, 29 Sep 2026 14:42:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:13d79ec2-0b00-408c-a82b-4d5e6b5a9dd7Testinghttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams-carTue, 29 Sep 2026 14:42:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:66704f83-5db3-43ec-9d96-7c5958785d0bhttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams-car-on-demandTue, 29 Sep 2026 14:42:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:47ccfb9c-5157-47c8-be8c-36f368bd605dhttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adamsTue, 29 Sep 2026 14:42:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:f41159a0-b99a-4aad-8c52-589492c72017https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/71823/design-time-interpolation-of-3d-akispl/1432835Mon, 14 Sep 2026 16:17:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:c5cd6f46-2100-4caf-8943-b24e6c1674d4michael.w.clarke1Hey Jesper. I've tried "linear" and its performance seems even worse for some reason. I created a test model w/ dummy spline data to test out a few different methods. "Spline" or "Cubic" with a transpose baked into them seem to be the most accurate (though they do overshoot a bit in some regions near the edges of the data. The table below summarizes a few cases I tested (green values are "correct", red are "incorrect"). I'm guessing the transpose is needed due to a difference in row/column major ordering between what Spline_1.y returns and what INTERP2 expects. No clue why linear performs so poorly as doing the same in MATLAB return reasonable results. Interp_Spline: (INTERP2(.MODEL_1.SPLINE_1.x, .MODEL_1.SPLINE_1.z, RESHAPE(.MODEL_1.SPLINE_1.y, {COLS(.MODEL_1.SPLINE_1.x), COLS(.MODEL_1.SPLINE_1.z)}), .MODEL_1.DV_Xval, .MODEL_1.DV_Zval, "spline")) Interp_Spline_Transpose: (INTERP2(.MODEL_1.SPLINE_1.x, .MODEL_1.SPLINE_1.z, TRANSPOSE(RESHAPE(.MODEL_1.SPLINE_1.y, {COLS(.MODEL_1.SPLINE_1.x), COLS(.MODEL_1.SPLINE_1.z)})), .MODEL_1.DV_Xval, .MODEL_1.DV_Zval, "spline")) Cmd file renamed as .txt to get around upload filter: nexus.hexagon.com/.../test_5F00_designtime_5F00_spline_5F00_interp.txthttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/71823/design-time-interpolation-of-3d-akispl/1432834Mon, 14 Sep 2026 14:23:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:a26c15b2-c845-4985-86b4-235c4c8c3149Jesper SlattengrenHi Mike, maybe unrelated, but last week I found a bug in INTERP1 that was making the "spline" option unstable. "cubic" works as expected. I don't know of this affects the INTERP2 function. Both of them are supposed to be clones of the corresponding MATLAB function. Have you tried the "linear" option?https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/71823/design-time-interpolation-of-3d-akispl/1432833Mon, 14 Sep 2026 11:21:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:9ff5b039-6429-4459-965f-253879147600michael.w.clarke1Digging this one back up. I am trying to accomplish the same trick of using INTERP2 to grab an AKISPL value at design time so I can initialize some inputs for a different simulation. For whatever reason INTERP2 is doing a poor job at interpolating the AKISPL data in this model. Are there any other alternatives to query an AKISPL at design time? I've tried: (INTERP2(myspline.x, myspline.z,reshape(myspline.y,{cols(myspline.x),cols(myspline.z)}),DV_1,DV_2,"cubic")) (INTERP2(myspline.x, myspline.z,reshape(myspline.y,{cols(myspline.x),cols(myspline.z)}),DV_1,DV_2,"spline")) Both of these return an incorrect value for a few test points. Using "nearest" does return a correct value, but DV_1 and DV_2 are being dispersed and could be intermediate points that aren't in the AKISPL data. (INTERP2(myspline.x, myspline.z,reshape(myspline.y,{cols(myspline.x),cols(myspline.z)}),DV_1,DV_2,"nearest"))https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams-car/74325/adams-car-leaf-spring-editor-using-inputs-based-on-design-height-geometry/1432821Mon, 17 Aug 2026 08:02:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:47240572-7ad8-41cf-bf24-883955bcd0f0Rishikesh MokashiHi The Leaf Spring Editor expects the X and Z coordinates to represent the leaf spring in its free (unloaded) state. During the makeleaf process, the spring is taken through three stages: free shape → rise-to-curb position (where the bushings are zeroed) → design position . If the geometry entered in the editor already represents the spring at design height, the model effectively starts from a pre-deflected condition. When vehicle weight is subsequently applied, the spring will deflect even further, resulting in additional flattening. Note- The Rise to Curb and Reference Marker to Leafpack parameters are only used to define the preload sequence. They do not convert the input geometry from one load condition to another. Possible approaches: Estimate the free shape geometry by offsetting the CAD Z-coordinates based on the expected deflection under the design load. This requires a reasonable estimate of spring stiffness and applied load. Adjust the Reference Marker height by specifying a slightly higher Z-value at the design-load condition. This can help compensate for the additional deflection and may be refined through a few iterations until the desired loaded shape is achieved.https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74330/convert-rwd-fsae_md_2010-cdb-template-to-4-motor-independent-awd-electric-fsae-vehicle/1432820Mon, 17 Aug 2026 03:46:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:23299519-d640-48f6-8131-4491dd19c2fcAlexis Del RioHi, Sorry for the confusion. We have a database for EV vehicles built in ACar: Adams Car Package > Adams Car > Working with Templates > aevhybrid_shared database Here you have a template/subsystem for wheel mounted motors and planetary gears (plus body mounted motors, hybrid engines...). You can select AWD/FWD/RWD. There is also a dedicated training ADM745 available. The motor subsystem may not plug directly into the FSAE model. If so, you will need to replicate those from the actual vehicle in the EV database. As Alex suggested is good practice to learn template and communicators. thanks, Alexishttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74330/convert-rwd-fsae_md_2010-cdb-template-to-4-motor-independent-awd-electric-fsae-vehicle/1432813Thu, 13 Aug 2026 11:29:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:efd2112c-06dc-4028-b6fc-4f59acff5ea4AS202601276131Hi, Thanks for the question. MSC Software is no longer part of Hexagon and is now a part of Cadence. We do not offer a four-motor template for Adams Car for Formula SAE. I encourage you to try learning template builder and making the template you need for your team. At the same time, template builder is for expert users. I recommend working through the e-learning for Adams Car and the built-in tutorials on template builder. Also, I see you're using the 2010 template. The latest version is available here: https://simcompanion.hexagon.com/customers/s/article/adams-car-for-fsae-main-directory-kb8020090 Sincerely, -Alexhttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74330/convert-rwd-fsae_md_2010-cdb-template-to-4-motor-independent-awd-electric-fsae-vehicle/1432812Thu, 13 Aug 2026 10:49:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:5669b31c-3575-452f-93c3-ad6849d15c0aMC202509189142Post moved from How to use Communityhttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74330/convert-rwd-fsae_md_2010-cdb-template-to-4-motor-independent-awd-electric-fsae-vehicleWed, 12 Aug 2026 20:04:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:45e11cbe-00db-4908-a27c-fd4cf7279690zhang jinhengI am using the official rear-wheel-drive FSAE template fsae_MD_2010.cdb in Adams/Car. All front suspension, rear suspension and steering subsystems have been modified for my electric FSAE race vehicle. My target layout is four independent wheel motors (4-motor AWD) : each wheel is driven by a separate electric motor. There is no internal combustion engine, no differential and no propeller shaft. I have two main questions: Does Hexagon provide an official ready-made 4WD / four-motor FSAE template for Adams/Car? If no official template is available, please offer detailed workflow or technical documents for powertrain reconstruction. Currently I meet two core difficulties: I do not know how to transform the original internal combustion engine powertrain subsystem into an electric motor-driven system. I need to build independent drive units for the front left, front right, rear left and rear right wheels separately. I lack guidance on subsystem duplication, communicator renaming to eliminate naming conflicts, and assembly matching for each wheel drive. I cannot find relevant tutorials so far. Thanks a lot for your technical support.https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams-car/74325/adams-car-leaf-spring-editor-using-inputs-based-on-design-height-geometryWed, 05 Aug 2026 13:23:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:b3490dba-4827-4e24-a018-340bc6c5af7ejsph_incHello, I am using the Leaf Spring Editor to create a leaf spring in ADAMS/Car. I have CAD of the leaf spring in the design height. CAD of the leaf spring in the unloaded position is not available. If I use this CAD for the leaf X-Z locations, is there a way to account for it being in design height (ADAMS expects these locations to be the unloaded position)? I've been trying to compensate for this through the "Rise to Curb" and "Reference Marker to Leafpack" values but no luck so far. After equilibrium the leaf springs have flattened which is not realistic. Thanks for any help! j.https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74279/mnf-generation-with-modal-stress-recovery/1432705Thu, 21 May 2026 03:02:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:8e6b2535-0b8d-4054-89b0-4b0bd0ad86d7MC202509189142Thread moved from How to use communityhttps://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74279/mnf-generation-with-modal-stress-recoveryWed, 20 May 2026 12:59:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:97cc9f03-1c83-4e0d-a976-75de570eace7matteo.franzeI have successfully created the MNF for a part containing RBE3 and glued contacts following article KB8022673 ( Generating Modal Neutral Files (MNF) using Nastran - Commands Explained ). The MNF has been imported into ADAMS, all loads and constraints defined and the dynamic simulation runs without issues. However, ADAMS does not show the stresses since they were not requested in Nastran. Now I am trying to modify the Nastran deck to request the grid point stresses following article KB8019006: How to create an MNF using Nastran The Nastran deck looks like this (lines highlighted are new) SOL 103 CEND ECHO = NONE METHOD = 1 ADAMSMNF FLEXBODY=YES TITLE = Modal Analysis SUBCASE 1 AUTOSPC(NOPRINT)=YES DISPLACEMENT(PLOT) = ALL STRESS(PLOT) = ALL STRAIN(PLOT) = ALL OUTPUT(POST) SET 9999 = ALL EXCEPT 1, 4, 6, 7, 9 THRU 41 VOLUME 12 SET 9999 DIRECT GPSTRESS (PLOT) = ALL GPSTRAIN (PLOT) = ALL BCONTACT=10000 $ $ BEGIN BULK $------1-------2-------3-------4-------5-------6-------7-------8-------9 DTI UNITS 1MGG N MM S PARAM AUTOQSET YES PARAM POST -1 PARAM AUTOSPC YES PARAM GRDPNT -1 PARAM K6ROT 0.0 PARAM MAXRATIO 1E+07 PARAM INREL 0 PARAM PRGPST YES PARAM OGEOM YES PARAM AUTOMSETYES $ EIGRL 1 20 MASS $ ASET 1590458 123456 1590459 123456 $ ASET 101 123456 102 123456 103 123456 104 123456 ASET 105 123456 106 123456 $ ASET 1001 123456 1002 123456 1003 123456 1004 123456 ASET 1005 123456 1006 123456 1007 123456 2001 123456 ASET 2002 123456 2003 123456 2004 123456 2005 123456 ASET 2006 123456 2007 123456 3001 123456 3002 123456 ASET 3003 123456 3004 123456 3005 123456 3006 123456 ASET 3007 123456 4001 123456 4002 123456 4003 123456 ASET 4004 123456 4005 123456 4006 123456 4007 123456 $ ASET 1 123456 where 1, 4, 6, 7, 9 THRU 41 are the IDs of the RBE3 and the nodes in the ASET are the dependent nodes of the RBE3. This simulation does not work, due to high pivot ratios. I tried to create CBEAM like the article says " If RBE3 element is present in the FEM model, neither the dependent degree of freedom may be defined as MASTER node, nor it may be assigned to another rigid element (RBAR or RBE2). Usually, as workaround, a new node is defined very close the MPC or RBE3 first node and connected to this through a CBEAM element (6 DOFs) with high stiffness in order to model a rigid-like connection " and include the CBEAM nodes in the ASET, as an example CBEAM 91590459 9999 91590459 1590459 1.0 0. -1.0 PBEAM 9999 9999 1.0E+4 1.0E+06 1.0E+06 MAT1 9999 2.1E+11 8.0E+10 0.3 0.0 but also this option is giving the same error. *** USER FATAL MESSAGE 10560 (SUBDMAP SEKR) During decomposition of matrix KOO, the degrees of freedom listed had pivot ratios greater than MAXRATIO. Verify that the degrees of freedom are not part of a mechanism and that elements do not have excessive stiffness. Does anyone has an idea how to fix it? I would like to avoid using RBE2 because the will add stiffness to the part...https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74266/torque-graph-simulation-of-non-conventional-bike/1432694Wed, 13 May 2026 12:34:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:71bfaf84-c1bc-4dc3-8e0a-ca4e703600c7Jesper SlattengrenFor a free-wheeling mechanism, I would suggest to use a one-sided stop (IMPACT) instead of the double-sided stop (BISTOP). And use velocity as the independent variable. IMPACT(WZ(M1,M2), WDTZ(M1,M2,M2),0.0, 1e8, 2.0, 1e5, 1d) for example. This will lock the rotation when the speed < 0.0.https://community.cadence.com/cadence_technology_forums/physical-system-simulation/adams/f/adams/74266/torque-graph-simulation-of-non-conventional-bike/1432690Tue, 12 May 2026 04:32:00 GMT75bcbcf9-38a3-4e2e-b84b-26c8c46a9500:e30261f4-4502-4147-bb88-600adf20e876Alexis Del RioIs this a recumbent bike?