I´m running an impact simulation however i´m getting unrealistics results. The simulation consists in a ball/plate impact, both of them steel material, ball is around 15 kg, the impact velocity is 7.6 m/s and gravity on favor. I´m using Johnson-cook to modelate both bodies but when I compare the results with the experimental data, for example the height of the first bounce, there are huge differences. At the experimental test, the ball bounced 83 mm aprox while in the simulation the maximun height it´s about 3 meters. What I noticed is that the velocity of the ball after the impact is about 3.9 m/s and I am using the values on the images at the Johnson-Cook parameters.

If there is anyone who could help me to understand why this is happening it would be really helpful.

Thank you

**BALL (A36)**

**PLATE (AR500)**

Best wishes,

Dr. Kazim Ahmet Hasim

]]>I just want to understand what is in the background for modal analysis so that I'm curious about effective mass ratio ...what is this ratio ? , what does it do ? , what does it mean ?

maybe this question could be very weird but from now thanks for your replies ..

]]>I hope that you are all doing well.

I am studying the vibration of a blade in function of rotational velocity. we suppressed the effect of aerodynamics

I used transient structural, assign the fixed support , Assign a rotational velocity

the blade feedback through ANSYS is presented in the picture.

Why the feedback is instantaneous in the numerical study while in the experimental it is a continuous sinusoidal (Measure with Laser vibrometry)?

Should I input Fixed rotation instead of fixed support?

Shall I also input the centrifugal force (rotation velocity is not enough?)

is there any thing wrong I am doing in the numerical analysis? how to compare in this case

]]>I was working my way through the cardiovascular stent exercise: https://courses.ansys.com/index.php/courses/cardiovascular-stent/ and am now attempting lesson 9. At first, I tried applying frictionless support on the 8 edges of the stent. However, this gave me rigid body motion errors. I'm not sure why.

I am afraid I do not know how to solve this now. Additionally, is it possible to do this exercise without the balloon? What supports/ constraints would work here? Any help is appreciated.

]]>For example, I have results for an assembly modelled in 5 scenarios, with maximum recorded vM stresses 0.15, 0.148, 0.16, 0.17 and 0.18 MPa. However, I want to set the maximum value for all them to 0.18 MPa, so that way I can directly compare the stress distribution between the 5 modelling cases. How do I do this?

I read on a forum that it isn't possible to change the maximum value. If this is the case, what software can I use to import the results and change the scale?

Thanks in advance!

]]>Im trying to set a model for sandwich panel composites to my project and it will includes a 3 point bending test. How can I describe a non lineer relation between supports and sandwich structure. I think constraint equations are giving a lineer relation between them.

Also I have a supports geometry so whichone should I use for my analysis.. Directly ansys's contacts and joints or contraint eq.?

]]>since the shared topology behaves as bonded contact, is it also possible to study debonding?

Thanks

]]>Whats the difference between total deformation and directional deformation if we modeled simple midspan load beam. I expect these two thinks give us a same result because there is only Y direction force effecting our beam but its not worked

cause I'am trying to set the model for sandwich structure, I just told you how I am try to think that model as simple as I can so that I gave a example for simple midspan beam

Best Regards

]]>I was trying to modelled sandwich panel composite beam for three point bending test but I dont know which theorem is ansys using for background by the way I am trying to find total displacement . Also should I modelled my composite face solid or sheel which one is the more accurate ? or should I modelled my core for solid and the other faces for sheel ?

Best Regards

]]>the material properties are of composite material of lay-up 0-90-0.

the material is orthotopic.

I want through the thickness graphs of the transverse shear and normal shear, in APDL or Workbench using 3D geometry.

like the above graph. (these graphs are drawn from another program).

Please suggest if anyone can help.

]]>Is it possible to know the equations for the development of the drilling dof in the shell 181 element? In particular, I would like to know some details about the strain-displacement relationships.

Your faithfully,

DM

]]>I would like to know some information about the physical distinction between the "spin softening" and the "stress stiffening", and where to find theoretical details.

Your faithfully,

DM

]]>A

]]>Here i varied the thickness of epoxy 7811G, keeping the size of Zeonex constant and boundary same.

the graph shows once the thickness is crossing 20, the stress are drastic and deformation is seen. what do i read of this.

how do i confirm if i am correct regarding this stress study, if i am wrong please point where i would have gone wrong.

for more info: Zeonex is standing on UV epoxy 7811G material

]]>I’m working on automatic analysis using python scripts. And I use the “External Data” system to transfer body temperature for my static structural model, as follows:

The problem I face is, after defining a ImportedBodyTemperature, how can I fill out the form in “Data View” panel of “Imported Body Temperature”.

Just like this:

I’ve searched API Guide, Help Document, Learning Form and Google. I only find:

ACT - Getting result time history: https://forum.ansys.com/discussion/comment/91825/

The python scripts I have now is :

# Define ImportedBodyTemperature Analysis = Model.Analyses[0] ImportedBodyTemperature = Analysis.Children[3].AddImportedBodyTemperature() ImportedBodyTemperatureDataView = Ansys.ACT.Interfaces.Mechanical.MechanicalPanelEnum.DataView ImportedBodyTemperatureDataView.Activate()

Thank you very much.

]]>I want to study a compressed beam in Ansys Mechanical APDL. To model the beam I used shell elements and MPC184 Elements (rigid beam), so that the beam extreme sections remain plane. he problem itself doesn't need any constraint, because it is auto-equilibrated, but to run the analysis on Ansys I need to prevent the rigid body motion (translations and rotations).

I chose to use the 3-2-1 method, constraining one edge in all three directions (x,y and z) (edge 1), another one in the directions y and z (edge 2), and the last one only in z direction (edge 3).

I supposed the flanges and the web 1 mm thick and I applied a pressure of 1 N/mm^2.

The problem is that if I use the MPC184 Elements and run a linear static analysis the stresses in x direction are not uniform, as shown in the figure below.

If I don't use the MPC184 Elements, but only the shell element on the flanges and on the web, the stresses are uniform.

**Why aren't the stresses uniform when I use the MPC184 Elements? How can i fix this?**

I need to simulate a sandwich beam, balsa wood core with carbon fiber in the top and bottom. This beam has variable cross section area, image below. After configuring the laminated material, I create the static structural analysis system, but when I add the configuration made in ACP, I only have the option to choose the shell or the solid. How could I run a simulation with the solid and shell together?

Boundary conditions: A fixed support, a XXXN of force; contacts between partA and B puls 12 screws.

Could u tell me im doing this simulation correct or not, here r some pictures of my settings below;

Coulld u tell me what happened in the force convergence? It seems not perfectly correct. I saw the deformation, stress results which seems fine. Just not sure about my NL analysis method correct or not.

Thanks a lot.

nonelinear structrual

nonelinear analysis

nonelinear analysis

nonelinear analysis

force convergence

after making a Eigen Buckling Analysis I want to update the geometry of my model with the deformation model of the fifth mode. How can I do it? I already know that I must use the command UPGEOM, but I don't know **** to select the mode of deformation which I refer to. I use Mechanical APDL. Thanks.

]]>I want to study a compressed beam in Ansys Mechanical APDL. To model the beam I used shell elements.

But, in order to run the analysis, I need to prevent rigid body motions of the beam. How can I do it? Which constraints should I use?

First I create a spring element type then I assign a real constant, after this I model two nodes and create an element, when applying a displacement there is no problem but when applying a load there is warning (see attached image).

Any idea on how to solve it?

Thank you in advance

Note: For older versions, there seems to be no issues.

]]>I would like to simulate a combination of electrostatic and structural analysis. Here I have attached the figure. In this fig blue box is a membrane and below surface act as a top electrode and red surface outline act as a bottom electrode. In between both electrodes, an air gap is there. I would like to apply a voltage between this electrode. since it has a non-uniform gap I can't choose emtgen command (the trans126) element. right?

I need this help in Ansys workbench. Could anyone please give me an idea about that how can I perform a combination of this analysis. I would like to membrane deflection after applying voltage.

Thanks and Regards,

Dhruvin

]]>I'm trying to simulate a sandwich beam, balsa wood core with carbon fiber in the top and bottom. The geometry is represented in the image below. Can I do this using midsurface? Or because of the variation in cross sectional area I treat the core as a solid?

I can add the nonlinear behavior in the "solution panel" for the static analysis in the panel of "solution control".

However, when i choose "harmonic" as analysis type, "solution control" panel does not appear in the "solution panel." And i can not run nonlinear harmonic analysis.

I kindly appreciate your helps.

Thanks in advance,

Mert

]]>I am trying to simulate a snap fit and the Pin. Where Tab is entering into the slot.

Both of them have the same material PC+ASA

I have worked with Non linear metals before but This is my first time working with Plastic material.

The Material is PC-ASA, I am attaching the material data sheet here. It has the Uniaxial tensile test results plotted.

So far I have defined non linear material with positive tangent for non linearity but here the material has a negative tangent and I am not sure how to define it in Ansys.

I manually entered uniaxial test results but seems the results are going way off.

I have very less idea of how to model plastics in ANSYS.

Can some one guide me through and direct me?

]]>I have been trying to solve stone masonry clock tower under scaled acceleration. The model was first created in SOLIDWORKS and then imported to ANSYS. The finite elements in the model are SOLID187 and there are 78000 elements in the model. The Drucker-Prager plasticity was involved. The model does not have any contact surface. Fixed support was used at the bottom of the tower. For the solution, I tried the following:

- I set 0.005 s, which is the recording interval of the acceleration record, as the analysis time step. Besides, I tried different time step values ranging from smaller values to larger ones.
- I used the Solver type for all possible options.
- I have changed the Newton-Raphson option from Program controlled to Unsymmetric.

Despite all this, unfortunately, I could not overcome the problem of convergence in the solution.

I would like to express that I would be grateful for any suggestions or help.

Best regards,

Şahin.

I am using Ansys workbench with the extension AddtitiveWizard.

From the guidelines, it is supposedly pop up AM transient thermal and AM static structural here but mine is not. is it the same? or will it affect the simulation?

Also, I cannot select the geometry for part and also base. I am curious because this seems to be very basic steps....

thank you in advance 😀 would appreciate the answer

]]>I am modeling concrete-filled GFR tube beam including prestressing tendons in ANSYS mechanical APDL R2. while after analysis my solution is not shown convergency and the load-displacement diagram is not realistic. How can fix these problems? Here I attached the convergence graph and the load-displacement of my analysis. I used CPT215 element for concrete, REINF264 for Reinforcement bar and prestressed tendons, Shell181 for GFRP tube, and solid 45 for support.

I kindly request you to help me

Thank You

The value of UY at node 1274 is 789090771. It is greater than the current limit of 1000000 (which can be reset on the NCNV command).

This generally indicates rigid body motion as a result of an unconstrained model. Verify that your model is properly constrained.

*** ERROR *** CP = 1.312 TIME= 22:10:28

*** MESSAGE CONTINUATION ---- DIAGNOSTIC INFORMATION ***

If one or more parts of the model are held together only by contact verify that the contact surfaces are closed. Also make sure that there are constraints (or friction) in the sliding direction even if no load is applied in that direction. You can use the CNCHECK command to check the initial contact status in the SOLUTION module.

]]>Im trying to performe an Harmonic analysis to a spring-damper-system and Im wondering what value should I assign to the BETAD coeff of my springs (Combin14 et). I think the formula is beta = csi/π/(f1+f2), so if my focus is on a particular frequency f*, i.e. one of the resonance frequencies, beta should be csi/2π/f*?

Thank you for your time

MB

]]>