Is there any document provided by ANSYS which explains how strain energy is determined in Static Structural?

]]>1) Is there any way to export my Workbench project as a batch file that I can solve on a separate machine? I need to a) export the batch file, b) find the command line entry to solve the batch file, and c) locate the solution file after solving.

2) Is there a way to edit my model in headless mode, i.e. using only a script editor? I especially want to be able to edit geometries, element types, and contact types. I have so far been able to find the Python script editor inside Mechanical, but I cannot find much documentation. If I could just work with APDL script without having to open Workbench, I think this would help a great deal.

Thanks for any directions or resources you can point me to!

]]>The fiber orientation of the laminates should follow the curved surface. How can I now specify that the application of the layers does not follow the curved surface, but a certain coordinate direction (such as the Z-direction)? Unfortunately, when I specify the direction as Z-direction (0,0,1) in the Oriented Selection Sets, it is oriented to the respective element orientation and not to the global Z-orientation. This means that my holes in ACP do not point in Z-direction but go 90° from the surface in an oblique direction. Do i have to specify some special reference direction rules?

I hope you can understand my problem a little bit.

]]>I am trying to apply pneumatic pressure into the middle chamber (small cube) to compress/close up the channel underneath but I have encountered the same error while doing so. The error is "The solver engine was unable to converge on a solution for the nonlinear problem as constrained".

The pressure setting used is (Type = Pressure), (Define by = Normal to), (Applied by = Surface Effect) to the faces of the chamber.

Fixed support applied at the bottom.

Large deflection was turned on and Capture proximity for mesh was also turned on.

Additional contact tool information:

I have also applied half-plane symmetry to reduce simulation time but the incomplete run took 10 hours to run.

Can anyone please advise on how to solve the error? Thanks in advance!

]]>I am using ANSYS 2019 R3, and my nonlinear adaptive mesh feature is inactive. Could anyone please let me know the solution to make it work?

]]>1.How do I put the Absorbing Boundary condition using Ansys2020 R1

M N RAY

]]>Biegespannung -> bending stress

Thanks a lot!

]]>First of all I am importing a surface map of temperatures to a body, applying some boundary conditions in terms of insulation and convection and I am investigating 1) the temperature in the center of the body and 2) the time evolution of the temperature in the whole body.

After that I am importing this temperature time evolution into the transient mechanical analysis. So far so good. The problem is that when I perform the simulation, the temperature is applied to the body at time 0 and the body deforms (expands) under this thermal load (picture 1). In my specific case however, the geometry I am importing is the already heated/deformed geometry and what I want to investigate is the contraction of the geometry as it cools down following the cooling process simulated in the first part.

Any idea if and how this could be implemented?

Thank you,

Aron

]]>I am trying to perform a parametric study on a cracked plate with these values being parametrized:

modulus of elasticity, yield stress, thickness, and the length of the crack as well as its transverse, longitudinal and angular position at the center of the plate.

The problem is that when I update parameters, some design points result in no values and are automatically neglected (most often those that in which the crack's angular orientation exceeds certain limits (less than 70 degrees and more than 100 degrees)). My initial guess is that I should do something about the mesh, but I have no idea about how to tackle that.

My initial mesh is a triangular mesh with 25mm size, and the crack edge meshed by hypothetically 20 elements.

This below picture shows the final model, but for now I am considering the XY plane with a crack at its center.

Ques 2 : Do we take into account the deformation also while transforming the coordinate system for non linear analysis solution?

]]>"The mesh generation did not complete due to poor quality elements or incorrect input. Please try meshing with another mesh method or different mesh options."

I'm running a Lenovo Legion 5 with:

- AMD Ryzen 5800H
- G.Skill RipJaws with 32 GB RAM (2 x 16 GB) running at 3200 MHz and CL22
- Nvidia RTX 3060 mobile

I've tested the same install files (the same zip) on a different machine. A desktop with:

- AMD Ryzen 3600X
- G.SKill RipJaws with 16 GB RAM (2 x 8 GB) running at 3200 MHz and CL16
- Nvidia GTX 1070

On this desktop machine everything is working as excepted (meshing works without errors).

I also uninstalled the complete Ansys package and removed every Ansys related directory and file I found and then reinstalled it (with reboots before and after every installation).

]]>**Here is the temperature distribution(I am using a dual heat source of Goldak type)**

**Constraints to restrain the rigid body motion**

At vertex C, all three displacements(x, y, z) are zero.

At vertex B, two displacements(x, z) are zero

At vertex A, one displacement(z) is zero

**This is the normal stress in the longitudinal direction(Y). I got**

welding time = 20sec and cooling time = 130 sec. Total 150sec simulation.

**And below is the expected pattern of residual stress.**

**My question:**

where am I possibly going wrong because my results are exactly the opposite of what is expected?

]]>I am using ANSYS 2021 R1 to calculate energy release rate for mode III.

The ANSYS fracture tool distribution of energy release rate is different when I obtain the energy release rate from nodal value directly. They are totally different at one side; moreover, there is a small difference between the values of Fracture tool and my calculation.

I have attached here both the values and graph.

Direct VCCT is the result of Fracture tool. In nodal VCCT, I export nodal force and displacement directly and calculate VCCT using the same formula that ANSYS uses.

ANSYS help for VCCT: https://ansyshelp.ansys.com/account/secured?returnurl=/Views/Secured/corp/v212/en/ans_frac/frac_parmcalctypes.html%23advvcctenrelrate

Does anyone have any suggestions about the root of this inconsistency and how I can solve it?

Thank you.

So i am working on a static structural analysis of a corner piece of a container unit. What i want to do is to recreate the experimental test results in which the corner piece was exposed to a force by a hydraulic cylinder ( the forces and horizontal displacements at the top of the beam at 1m from the test are shown in the attached picture), these forces created by the hydraulic cylinder represent the wind load on the container in which case the container corner ''opens'' ( see attached picture).

Im think that my contacts are set right but somehow im not getting the results i want. I used a 2 step analysis first for the pretension and the second for the remote displacement.

So my question is how can i recreate the simulation in which the results will be the most realistic, in which i will get the maximum moments on the beam and same reaction forces as in the tests. I think the problem lies somewhere in my boundary conditions but at this point im not sure, so if anyone can point me in the right direction i will be thankful.

Greetings

I'm trying to model battery nail penetration test in Mechanical. Below is the geometry and the blue structure is the trigger cell. I have an internal heat generation as an input in that structure that simulates the thermal runaway of the cell. I want to calculate the transient temperature distribution from this runaway. The problem is that the rest of the battery cells will also trigger an internal heat generation rate if the cell's temperature reaches a certain value. Is it possible to define an internal heat generation rate that is triggered at a certain temperature?

Thanks!

Can anyone assist with decreasing this time to a reasonable timeframe. I am using a High Performance Computer (HPC) system and they set my termination time for 4 days so I have a time constraint.

My experience is that for FEA, it is comfortable to mass scale without changing the accuracy by much, as long as the KE is less than 10% of the Total Energy. However, given the Kernel Function used in SPH has relation to the mass of particles for momentum and continuity requirements, I am almost certain that the answer will be altered significantly, but I can be wrong.

Please advise anyone,

Thanks

SS

]]>I'm doing the harmonic analysis of langevin transducer, but the deformation results is not what i expected. The amplitude in the front surface of the transducer should be about 5um.

This is the result.

This is the set-up for piezoelectric body.

This is the applied voltage-20V.

I am trying to simulate the stiffness of a curved composite tube. I am stuck in setting up ACP Pre as I can't get the fibre orientation right. The goal is to set a 90-degree ply along the curvature of the tube.

What I have done now:

- see the screenshot for the geometry orientation. The red line separates the geometry to its left and right.

- created a top down no symmetry [+-90] stackup with UD prepreg
- sectioned the tube from the centre line and defined three element sets: 'all elements', 'left', 'right'
- defined two edge sets using 'left' and 'right' element sets
- defined two edge wise rosettes using 'left' and 'right' edge sets, 1 direction (0, 1, 0), 2 direction (1, 0, 0)
- created an oriented selection set using 'left' and 'right' element sets and rosettes, selection method is min. angle, the origin point is set to be the green element in the screenshot above
- created modeling ply 1 using the OSS and the [+-90] stackup

I then generated the plies to see the fibre orientation created. The fibre orientations are supposed to be like the illustration below, where fibres are 90 degrees (perpendicular) to the tube's centre neutral axis in the direction of the yellow arrows:

When generated, the right side of the tube (the side shown above) has the correct fibre orientation, but the left side is very funny. At both ends of the tube on its left side, there is a triangular area where the fibre orientation is 0 degree (parallel to the centre neutral axis) as shown in the screenshots below. This is only happening on the left side while the right side is perfect for what I want.

Does anyone have a clue on what I have done wrong or what I can do to correct this?

Also, please teach me if there is a better way to model curved structures in ACP.

Thanks in advance!

]]>Thanks,

-Sami

]]>I'd like to suppress specific rigid remote points at certain load steps.

Is that in any way possible? (e. g. via command snippet)

Kind Regards

]]>I have checked all the associated parameters like contacts, gasket LD curves, etyc and they seem to be well. So could you suggest any possible solution/ reason for such high preload gain ?

Thanks,

Abhilash

]]>There are times where I like to apply a small displacement to a part to pre-load it, then switch to a force for the final target load. To do this in APDL, you specify FORCE as the ramping key on DDELE in the second step. Is there anyway to do this directly in the Mechanical GUI (other than by using APDL command snippets)

Thanks,

Nicoli

]]>Is there any expert to inform me please what is the difference between considering CSOLID, BEAM188 vs. PIPE288 as element type of the structure?

Appreciate

]]>i want to Export the Tabular Data of Frequency Responses. Because it is kind of exhausting to export all of these (about 200 Responses!) i want to write a Python Script or a Snippet, which exports automatically these Tabular to txt or Excel. Can Anybody help me?

Regards,

Florian Kiss

I want to show the effects on pressure and force only on the piston. How can I do so?

**OR**

Do I have to 2 different analysis-

1)One analysis showing only the action of the force with the pressure side as fixed support and

2)The second analysis showing only the action of pressure with the force side as fixed support ?

Thanks in advanced,

ZHSBEI

]]>Error is as followed:

'Gyroscopic matrix has been activated (RefFrame = ON on the CORIOLIS command) for rotating structure dynamics. When rotor spin is input through the CMOMEGA command, the element axis must be along the spin axis of the element component'

Attaching an archive. Please have a look at the model.

If anyone could help regarding this?

Thanks

]]>Recently, I am trying to simulate a orthotropic plane in ANSYS using SHELL181. The APDL input is as follows:

finish

/clear

/prep7

*afun,rad

et,1,shell181

sectype,1,gens,,bandanyuan,

sspa,420626,126188,,4.24713e8,,,

sspd,43.6662,13.0999,,48446.7,,30.6256,

sspe,,8.15102e7,

k,1,0,0,0

k,2,2.31,0,0

l,1,2

cm,tra,line

k,3,0,0,-12.164

l,1,3

adrag,tra,,,,,,2

allsel,all

mshape,0

mshkey,1

aatt,1,1,1,,1

amesh,all

!D11

allsel,all

lsel,s,loc,x,0

dl,all,,ux

dl,all,,uy

dl,all,,uz

dl,all,,rotx

dl,all,,roty

dl,all,,rotz

allsel,all

allsel,all

lsel,s,loc,x,2.31

dl,all,,ux

dl,all,,uy

dl,all,,uz

dl,all,,rotx

dl,all,,roty

dl,all,,rotz,1/50

allsel,all

When I ran the code, I got the following error messages:

*** NOTE *** CP = 10.374 TIME= 15:46:05

Predictor is ON by default for structural elements with rotational

degrees of freedom. Use the PRED,OFF command to turn the predictor

OFF if it adversely affects the convergence.

*** ERROR *** CP = 10.374 TIME= 15:46:05

Membrane stiffness of Element 10 (integration point 1) at temperature 0

is not positive definite.

*** ERROR *** CP = 10.374 TIME= 15:46:05

Shear stiffness of Element 10 (integration point 1) at temperature 0 is

not positive definite.

*** ERROR *** CP = 10.374 TIME= 15:46:05

Membrane stiffness of Element 12 (integration point 1) at temperature 0

is not positive definite.

*** ERROR *** CP = 10.390 TIME= 15:46:05

Shear stiffness of Element 12 (integration point 1) at temperature 0 is

not positive definite.

It seems that some material stiffness was not well defined. Can anyone give some suggestions about how to solve this problem?

Thank you very much!

Kind regards,

ceHumaNait

]]>

But if you set the air, what is the condition? Is attached.

Is there a solution?

]]>I simulated the uni-axial compression of an aluminium cylinder using Static Structural on Ansys Workbench.

In the solution section, the stress-strain plot and total defamation seem to be fine. But, when I want to see the total deformation as an animation on my model, it does not work properly and I cannot see the compression of my model up to the selected displacement (I selected the strain value of almost 50% for this simulation).

Can you please advice me in this regard?

Thank you.

]]>I have made some simulations in the Explicit dynamics workbench, and I need to couple this simulation result into a Transient thermal workbench to study the effect of temperature by applying convection and heat flux parameters. However, the Explicit dynamics workbench result or solution is not couple to the Transient thermal workbench. Is there is any solution to solve this problem?

]]>I am trying to simulate bending of soft gripper, just like on the image below:

I've already built a geometry of the gripper and I've assigned proper materials to each component. Three components are made of Dragon Skin 20. They have stifness behaviour defined as flexible.

And there is another body, thin layer made of paper. Its stifness behaviour is defined as rigid.

Below, you can see properties of each material.

**Dragon Skin 20:**

**Paper:**

I've generated mesh and I've inserted a pressure that is applied on the interior of the soft gripper.

What type of constraints should be added? And on what bodies/surfaces should they act? Details of Analysis Settings are attached below:

I'm using ANSYS Academic Student 2019 R2.

I'm stuck, I will be very grateful for every hint.

]]>/PREP7

ET,1,BEAM188

MPTEMP,,,,,,,,

MPTEMP,1,0

MPDATA,EX,1,,2.068e11

MPDATA,PRXY,1,,0.3

MPTEMP,,,,,,,,

MPTEMP,1,0

MPDATA,DENS,1,,7830

SECTYPE, 1, BEAM, RECT, Beam01, 0

SECOFFSET, CENT

SECDATA,0.01,0.01,2,2,0,0,0,0,0,0,0,0

K,1,0,0,0,

K,2,1,0,0,

LSTR, 1, 2

LESIZE,ALL, , ,8, ,1, , ,1,

LMESH, 1

FINISH

/SOL

ANTYPE,2

MODOPT,LANB,8

EQSLV,SPAR

MXPAND,8, , ,0

LUMPM,0

PSTRES,0

MODOPT,LANB,8,0,0, ,OFF

FLST,2,1,1,ORDE,1

FITEM,2,1

/GO

D,P51X, , , , , ,ALL, , , , ,

/STATUS,SOLU

SOLVE

which gives the perfect results. However, the same problem in workbench with 42 elements does not give the results, why is that? What should I do with the meshing in workbench?

I was using the FSI (Ansys platform) to simulate the flow through a deformable vessel. The FSI contains three modules, which are “Transient Structure”, “Fluent,” and “System Coupling” (see Fig.1). The Fluent has periodic boundary conditions, and Structural analysis utilized the elastic material model.

Fig.1 Frameworks in WB.

Unfortunately, an error of “negative cell volume” comes up in the first few time steps ( t = 0.02s), see in Fig.2.

Fig.2 Detected negative cell volume during the iteration.

To detect the problem, I ran the Fluent standalone (with a rigid vessel wall) and found that the maximum pressure on the vessel wall is around 6000 Pa. (I added a pressure = 5332Pa at the outlet. That is why the pressure in the figure below is not 0 pa at the outlet)

Fig. 3 The pressure contour and maximum pressure distribution on the vessel wall over time.

Therefore, I loaded the compliant vessel in the Transient Structure (standalone) with a pressure of 9000 Pa. It seems the compliant vessel can take this pressure:

Fig. 4 Pressure load on the vessel wall.

I also used EnSight to load the FSI data before the error came up. I found the vessel wall deformation was extremely large in one direction.

Fig. 5 The force distribution of the vessel before the simulation stops.

Since the error comes up at the beginning of the simulation (t = 0.02 s), the maximum pressure at this time (based on Fig. 3) should be around 5500 Pa, less than the one I used for Structural Analysis (in Fig. 4).

I also ran with different time step sizes (changed from 0.01 to 0.001), but the error still comes up at t = 0.02 s. Later, I also repeated the simulation using different FSI step control settings (minimum and maximum iterations changed from 1 to 5, and 5 to 20 respectively) and the error comes up at t = 0.08 s. Then, I activated the ramping from “None” to “Linear to Minimum Iteration” and ran the simulation again (See Fig. 6). Unfortunately, the same error occurs at t = 0.16 s.

Fig. 6 Ramping settings in System Coupling.

I am not sure what to check next. Could you please provide some insights?

Best regards,

Ya

]]>