Nabble - Abaqus Users

How much does using Virtual Memory (Page files) decrease performance in Abaqus?

2009-11-10T23:30:05Z

So I have 16GB of physical memory, but the analysis I need to run has about 8 million quadratic hybrid tetrahedral elements, which is requiring about 43 GB of space right now. The value peaked at about 70GB, when I think Abaqus was building the B matrix. I have two dual-core 3.1GHz AMD Opteron processors running on Windows XP Pro x64.However, now that I'm using virtual memory, only one processor is pegged (25%), which is being used by a program called "standard.exe" (part of Abaqus).

I submitted the job, which is supposed to give me only basic stress and displacement information, on 11/7/09 at 6:22AM (about 84 hours ago) and it has still not finished. Earlier, I ran a analysis that had 2 million elements and it took up about 18GB of memory and took about 2 hours to complete using all 4 processors.

Right now, under the "processes" tab of the task manager, standard.exe is only using 200k memory, and is maxing out one CPU only. However, under the performance tab, it says that 68.2GB are being used. What's really odd, is that it appears Abaqus isn't using any of my physical memory any more, only virtual memory. I have nine 15,000rpm Seagate Cheetah hard drives that I split the page files onto, hoping that would improve my performance. I wish I had the $4000 it would cost to upgrade to 64GB of RAM, but I don't...

So my question is, is this thing ever going to finish? This week, this month? Should I just give up?

Is there any way to tell how long it might take by knowing how many elements there are?

How much slower should this take using the type of hard drives I have instead of using physical memory?

Does it help or hinder me to split the page files onto different drives?

Is there anything else besides reducing the amount of elements that will make this work?

Thanks in advance for the help!

Re: Erase(Hide) meshes in visualization mode!!!

2009-11-10T15:32:11Z

On the "Basic" tab of the "Common Plot Options" dialog box you can find
a variety of options for "Visible Edges". Try "Feature edges", "Free
edges", or "No edges".

Regards,

Dave

-------------------------
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

Victor wrote:

>
>
>
>
> Hi all,
>
> is it possible to erase mesh in Visualization mode and only show the contour
> plot?
>
> I want to show an overview of my model. Because there are coarse and fine
> meshes in it, the fine meshes are absolutely dark and graph is not clear.
>
> Any idea will be appreciated.
>
> Regards
>
> Victor
>
> [Non-text portions of this message have been removed]
>
>

------------------------------------

Community email addresses:
Post message: Abaqus@...
Subscribe: Abaqus-subscribe@...
Unsubscribe: Abaqus-unsubscribe@...
List owner: Abaqus-owner@...

Shortcut URL to this page:
http://groups.yahoo.com/group/AbaqusYahoo! Groups Links

<*> To visit your group on the web, go to:
http://groups.yahoo.com/group/Abaqus/

<*> Your email settings:
Individual Email | Traditional

<*> To change settings online go to:
http://groups.yahoo.com/group/Abaqus/join
(Yahoo! ID required)

<*> To change settings via email:
Abaqus-digest@...
Abaqus-fullfeatured@...

<*> To unsubscribe from this group, send an email to:
Abaqus-unsubscribe@...

<*> Your use of Yahoo! Groups is subject to:
http://docs.yahoo.com/info/terms/

Re: Erase(Hide) meshes in visualization mode!!!

2009-11-10T15:23:46Z

Hi Victor,

In the Visualization, Go to

Options -> Common -> Basic tab

Under 'Visible Edges', Switch from 'Exterior Edges' to 'Feature Edges'

Best,
NS

2009/11/10 Victor <goldman1378@...>

>
>
>
>
> Hi all,
>
> is it possible to erase mesh in Visualization mode and only show the
> contour
> plot?
>
> I want to show an overview of my model. Because there are coarse and fine
> meshes in it, the fine meshes are absolutely dark and graph is not clear.
>
> Any idea will be appreciated.
>
> Regards
>
> Victor
>
> [Non-text portions of this message have been removed]
>
>
>

[Non-text portions of this message have been removed]

Re: Thickness Reduction of Shell Elements

2009-11-10T12:52:22Z

Hi,

There is no option to switch off contact reduction for all shell elements in
a model, but you can reduce number of elements for which Abaqus will made
reduction. To do it you need to use keyword:
*CONTACT CONTROLS ASSIGNMENT, CONTACT THICKNESS REDUCTION=SELF
or
*CONTACT CONTROLS ASSIGNMENT, CONTACT THICKNESS REDUCTION=NOPERIMSELF
For more information please take a look to documentation, chapter 30.3.6
CONTACT CONTROLS FOR GENERAL CONTACT IN Abaqus/Explicit, Control of contact
thickness reduction checks.

To plot contact thickness in general contact you can use field output
CTHICK.

Regards,
Bartosz

Nan Guofeng wrote:

Dear all,

I'm now simulating tube crushing with Abaqus/Explicit. The tube is meshed with shell elements, and general contact is used for contact. As the mesh goes finer, the thickness of elements reduces and there's a warning message as follows:

In step 1, some facet thicknesses for general contact were reduced
            from the parent element or specified values due to a large
            thickness compared to facet dimensions. The most significant
            thickness scaling factor was 0.39114 for a facet on parent element
            5772 of instance ETA_25-1. An element set named
            "WarnElemGContThickReduce" has been created for use in
            ABAQUS/Viewer to locate the regions of reduced thickness.

I know that such thickness reduction is required by the contact simulation, but can anyone give some comments on to what extent such reduction will influence the final results? and is it possible to know the amount of thickness reduction for each element whose thickness has been reduced. (As the warning message only gives the most significant reduction value).

Many thanks and kindly regards,

Song J.

___________________________________________________________
好玩贺卡等你发，邮箱贺卡全新上线！
http://card.mail.cn.yahoo.com/

[Non-text portions of this message have been removed]

How can we get history output in a cylindrical coordinate?

2009-11-10T09:32:45Z

Hi everyone,
I am writing to know how can we get history output in a cylindrical
coordinate? I want element stresses expressed in a cylindrical coordinate
rather than the global RECTANGULAR one. I had several try
with "*ORIENTATION, NAME=name, SYSTEM=CYLINDRICAL" for parts and assembly
respectively, and it seems there are no influence on the histrory output.
Can anybody help me on this? Thanks in advance!
Xinke

[Non-text portions of this message have been removed]

Converge Issues using *KINEMATIC COUPLING

2009-11-10T09:17:44Z

Dear all,

Has anybody encountered convergence issues when using *KINEMATIC COUPLING?

Here's my problem:

I am doing a nonlinear (Material only, *PLASTIC) quasi-static analysis on a engine cradle.

The model is made of S4 and S3 elements.

Loads are applied remotely (at the bushing mounts) and transferred onto the cradle using *KINEMATIC COUPLING (DOF 1 thru 6).

The analysis has some converging issues right from the start (does not complete the first time step). Keeping all parameters constant, I changed *KINEMATIC at one location and replaced it with C3DX elements. The simulations seemed to be more stable, but still fails to converge after t step not equal to zero.

Any comments?

Can this be load transfer be modeled using *EQUATION instead?

Your help is much appreciated.

Thank you,
Sacheen
Graduate Student
McGill University

Erase(Hide) meshes in visualization mode!!!

2009-11-10T08:13:38Z

Hi all,

is it possible to erase mesh in Visualization mode and only show the contour
plot?

I want to show an overview of my model. Because there are coarse and fine
meshes in it, the fine meshes are absolutely dark and graph is not clear.

Any idea will be appreciated.

Regards

Victor

[Non-text portions of this message have been removed]

Re: flywheel

2009-11-10T05:29:09Z

2009/11/9 Abdullah Alshammari <a.alshammari1981@...>

>
>
>
>
> Hello to all,
> Maybe my question is very sample for you but really hard for me.
> What is the best way to sketch the flywheel drawing into Abaqus.
>
> Regards
> albader
>
>

Sketch module in Abaqus works like a CAD program. You can draw a lot of
defult lines (like circles, squares, etc..), else you can import a DXF file
from AutoCad.
In conclusion, if you are good in AutoCAD draw you can do the flywheel there
and then import it in the sketch module in Abaqus. Pay attention: because
you can only import 2D images with the Sketch Module.

Bye

Nicholas

[Non-text portions of this message have been removed]

UELMAT plane stress

2009-11-10T04:45:38Z

Hello to all,
I'm working on implementing plane stress problem in UELMAT, but Unfortunately there is no example in ABAQUS.
Do you have access to ABAQUS algorithm for elasto-plastic plane stress problems or any example for plane stress implementing in UELMAT.
Best regards

flywheel

2009-11-09T13:32:01Z

Hello to all,
Maybe my question is very sample for you but really hard for me.
What is the best way to sketch the flywheel drawing into Abaqus.

Regards
albader

Re: Strain Output with Python Script

2009-11-09T11:28:32Z

I'm not sure if you can directly access the averaged nodal value or not.
However, if you have the element nodal values, you can certainly
calculate them.

Regards,

Dave

-------------------------
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

alper güner wrote:

>
>
> Dear members,
>
> is it possible with Python to obtain the averaged Strain Outputs
> (PE11,PE22) at the nodes?
>
> When I set the location as NODAL, I can not get the data (the code does
> not work, I suppose). ELEMENTAL NODAL has only the extrapolated values
> from the integration points,as far as I can see. Thank you in advance.
>
> Alper
>
> [Non-text portions of this message have been removed]
>
>

Re: PLot Graphs

2009-11-09T05:39:39Z

Just save these both graphs which you have plotted against time. Press Create X-Y and for the plot options select Operate on X-Y data there you can use "Combine option" to plot stress-strain on a single graph.
regards,

Farasat Iqbal
Msc.-Engr. Materials Science
Institute of General Materials Properties
University of Erlangen-Nürnberg
Germany
Office +49 9131 85-27478
Mobile +49 176 24643124
E-mail Farasat.iqbal@...

________________________________
From: Niyotha Henen <hniyotha@...>
To: Abaqus@...
Sent: Mon, November 9, 2009 11:58:14 AM
Subject: [Abaqus] PLot Graphs

Dear Abaqus Users
I plotted a graph in abaqus wrt to stress,strain in y axis and time in x axis

how can we change the graph with stress on y axis and strain on x axis

Thanks
Niyotha

From cricket scores to your friends. Try the Yahoo! India Homepage! http://in.yahoo. com/trynew

[Non-text portions of this message have been removed]

[Non-text portions of this message have been removed]

Re: linking UMAT through Abaqus\CAE

2009-11-09T05:15:51Z

Hi amr,

you can give the directory of your UMAT-file when defining your job in the 'General' tab of the 'Edit job' window.

Cheers
Fabian

Re: PLot Graphs

2009-11-09T04:27:55Z

Niyotha,

In ToolsXY Data*CreateOperate on XY-data, use 'combine' option.*

Best,
NS

2009/11/9 Niyotha Henen <hniyotha@...>

>
>
> Dear Abaqus Users
> I plotted a graph in abaqus wrt to stress,strain in y axis and time in x
> axis
>
> how can we change the graph with stress on y axis and strain on x axis
>
>
> Thanks
> Niyotha
>
> From cricket scores to your friends. Try the Yahoo! India Homepage!
> http://in.yahoo.com/trynew
>
> [Non-text portions of this message have been removed]
>
>
>

[Non-text portions of this message have been removed]

Re: linking UMAT through Abaqus\CAE

2009-11-09T04:19:38Z

When you create a Job, then go to General tab of the Job editor. It has a
place to link your .for UMAT file.

Best,
NS

2009/11/7 amr guaily <amrgamal73@...>

>
> Hi all,
> I'm on my way to build a UMAT. My question is how to link this UMAT fortran
> file to Abaqus through the Abaqus\CAE. I tried by
> double clicking on Materials, then I choose USER Material, but I couldn't
> figure out how to link the UMAT fortran file to the material. I hope my
> question is clear and sorry if it is trivial as I'm new to Abaqus.
>
> your help is greatly appreciated.
> waiting for your reply,
> amr
>
> P.S. I know how to use the command line (abaqus job=jobname user=user
> subroutine)
>
>
> _________________________________________________________________
> Windows Live: Make it easier for your friends to see what youre up to on
> Facebook.
> http://go.microsoft.com/?linkid=9691816
>
> [Non-text portions of this message have been removed]
>
>
>
> ------------------------------------
>
> Community email addresses:
> Post message: Abaqus@...
> Subscribe: Abaqus-subscribe@...
> Unsubscribe: Abaqus-unsubscribe@...
> List owner: Abaqus-owner@...
>
> Shortcut URL to this page:
> http://groups.yahoo.com/group/AbaqusYahoo! Groups Links
>
>
>
>

[Non-text portions of this message have been removed]

------------------------------------

Community email addresses:
Post message: Abaqus@...
Subscribe: Abaqus-subscribe@...
Unsubscribe: Abaqus-unsubscribe@...
List owner: Abaqus-owner@...

Shortcut URL to this page:
http://groups.yahoo.com/group/AbaqusYahoo! Groups Links

<*> To visit your group on the web, go to:
http://groups.yahoo.com/group/Abaqus/

<*> Your email settings:
Individual Email | Traditional

<*> To change settings online go to:
http://groups.yahoo.com/group/Abaqus/join
(Yahoo! ID required)

<*> To change settings via email:
Abaqus-digest@...
Abaqus-fullfeatured@...

<*> To unsubscribe from this group, send an email to:
Abaqus-unsubscribe@...

<*> Your use of Yahoo! Groups is subject to:
http://docs.yahoo.com/info/terms/

Beam: cross-sectional scaling factor ?

2009-11-09T03:07:48Z

Hello group,

we want to understand how ABAQUS computes the bending moment in a beam element.

The theory manual provides an equation following the line
'We now introduce the generalized section forces as defined below:'

This equation depends on f, which is defined as a 'cross-sectional scaling factor'. That definition is provided right at the beginning of the chapter entitled '3.5.2 BEAM ELEMENT FORMULATION'.

From
'the cross-sectional coordinates S_alpha, which are assumed to be distances measured in the original (reference) configuration of the beam'
and requiring consistent units it can be inferred that f is a constant (as the difference in S_beta - S_beta_c must be a factor in order to arrive at Newton*meter for the moment, so this difference is not meant to be a parameter for f).

Can anyone give me a clue how this 'cross-sectional scaling factor' is to be computed in the course of the deformation ?

Thank you for your expertise in advance,

Frank
--
-----------------------------------------------------------------------
Frank Richter
Institute of Materials Science
Ruhr-Universitaet Bochum
Bochum
Germany

DSL-Preisknaller: DSL Komplettpakete von GMX schon für
16,99 Euro mtl.!* Hier klicken: http://portal.gmx.net/de/go/dsl02

PLot Graphs

2009-11-09T02:58:14Z

Dear Abaqus Users
I plotted a graph in abaqus wrt to stress,strain in y axis and time in x axis

how can we change the graph with stress on y axis and strain on x axis

Thanks
Niyotha

From cricket scores to your friends. Try the Yahoo! India Homepage! http://in.yahoo.com/trynew

[Non-text portions of this message have been removed]

Thickness Reduction of Shell Elements

2009-11-08T22:45:33Z

Dear all,

I'm now simulating tube crushing with Abaqus/Explicit. The tube is meshed with shell elements, and general contact is used for contact. As the mesh goes finer, the thickness of elements reduces and there's a warning message as follows:

In step 1, some facet thicknesses for general contact were reduced
            from the parent element or specified values due to a large
            thickness compared to facet dimensions. The most significant
            thickness scaling factor was 0.39114 for a facet on parent element
            5772 of instance ETA_25-1. An element set named
            "WarnElemGContThickReduce" has been created for use in
            ABAQUS/Viewer to locate the regions of reduced thickness.

I know that such thickness reduction is required by the contact simulation, but can anyone give some comments on to what extent such reduction will influence the final results? and is it possible to know the amount of thickness reduction for each element whose thickness has been reduced. (As the warning message only gives the most significant reduction value).

Many thanks and kindly regards,

Song J.

___________________________________________________________
好玩贺卡等你发，邮箱贺卡全新上线！
http://card.mail.cn.yahoo.com/

[Non-text portions of this message have been removed]

ADJUST ONLY TO REMOVE OVERCLOSURE

2009-11-08T22:35:13Z

Hello Everyone

I am running a simulation consisting of 3 rectangular plates which are held together by two bolts (modeled as two cylinders without any bolt head). I noticed that while defining interactions, when i select the option "ADJUST ONLY TO REMOVE OVERCLOSURE " the Stresses which i get in the xx and yy direction are very different when i run the simulation without selecting this option. Can any one please tell me why this is happening ?. I am using a friction coefficient of 0.05 while defining the interactions.

When I define the interaction property as frictionless the run bombs out by giving out an error " Too many attempts made for this increment ", is this because of rigid body motion. Please can some one give me your comments/suggestions on this, it would be very helpful. Thank you.

Aneesh

Strain Output with Python Script

2009-11-08T12:16:44Z

Dear members,

is it possible with Python to obtain the averaged Strain Outputs (PE11,PE22) at the nodes?

When I set the location as NODAL, I can not get the data (the code does not work, I suppose). ELEMENTAL NODAL has only the extrapolated values from the integration points,as far as I can see. Thank you in advance.

Alper

[Non-text portions of this message have been removed]

linking UMAT through Abaqus\CAE

2009-11-07T20:32:16Z

Hi all,
I'm on my way to build a UMAT. My question is how to link this UMAT fortran file to Abaqus through the Abaqus\CAE. I tried by
double clicking on Materials, then I choose USER Material, but I couldn't figure out how to link the UMAT fortran file to the material. I hope my question is clear and sorry if it is trivial as I'm new to Abaqus.

your help is greatly appreciated.
waiting for your reply,
amr

P.S. I know how to use the command line (abaqus job=jobname user=user subroutine)

_________________________________________________________________
Windows Live: Make it easier for your friends to see what youre up to on Facebook.
http://go.microsoft.com/?linkid=9691816

[Non-text portions of this message have been removed]

------------------------------------

Community email addresses:
Post message: Abaqus@...
Subscribe: Abaqus-subscribe@...
Unsubscribe: Abaqus-unsubscribe@...
List owner: Abaqus-owner@...

Shortcut URL to this page:
http://groups.yahoo.com/group/AbaqusYahoo! Groups Links

<*> To visit your group on the web, go to:
http://groups.yahoo.com/group/Abaqus/

<*> Your email settings:
Individual Email | Traditional

<*> To change settings online go to:
http://groups.yahoo.com/group/Abaqus/join
(Yahoo! ID required)

<*> To change settings via email:
Abaqus-digest@...
Abaqus-fullfeatured@...

<*> To unsubscribe from this group, send an email to:
Abaqus-unsubscribe@...

<*> Your use of Yahoo! Groups is subject to:
http://docs.yahoo.com/info/terms/

Re: Multi step - Implicit and Explicit

2009-11-06T13:39:22Z

Hi Everyone,

Thanks for your response. I think *IMPORT is the way to go for me as I dont have Abaqus6.9. Thank you once again.

Regards

Maajid

--- In Abaqus@..., Arvind Chakravarthi <arvindinus@...> wrote:

>
> Hello Maajid,
> Â
> At the moment it is not possible to exactly do the way as you requested ("I wanted to know if it is possible to have step 1 as STATIC IMPLICIT and step 2 as DYNAMIC EXPLICIT in a single input file? ")
>
> Abaqus 6.9 has this *IMPORT feature where in the results state of a simulation can be imported on to the next simulation. In your case the result state from the IMPLICIT analysis must be imported on to the EXPLICIT simulation.
> Â
> Another feature that is special to the 6.9 release is the IMPLICIT_EXPLICIT co-simulation which does not serve your purpose.
> Â
> For further info on the *IMPORT functionality, read through the following
> Â
> Transferring results between Abaqus analyses: overview,â Section 9.2.1 of the Abaqus Analysis User's Manual
> Â
> Hope this helps
> Â
> Andy
> Â
> Â
> Â
> Â
>
> --- On Wed, 11/4/09, CABROL Eric (renexter) <eric.cabrol-renexter@...> wrote:
>
>
> From: CABROL Eric (renexter) <eric.cabrol-renexter@...>
> Subject: RE: [Abaqus] Multi step - Implicit and Explicit
> To: "Abaqus@..." <Abaqus@...>
> Date: Wednesday, November 4, 2009, 6:25 AM
>
>
> Â
>
>
>
> It will be possible with version 6.9
> (http://www.simulia. com/download/ pdf/Abaqus69_ Addendum_ final.pdf)
>
> Eric
>
> -----Message d'origine--- --
> De : Abaqus@yahoogroups. com [mailto:Abaqus@yahoogroups. com] De la part de maajidchishti
> EnvoyÃ© : mercredi 4 novembre 2009 01:20
> Ã : Abaqus@yahoogroups. com
> Objet : [Abaqus] Multi step - Implicit and Explicit
>
> Dear All
>
> I need to model a single lap joint loaded under tension. In this model I have apply a bolt load using Pretension surface and I am using a VUMAT for prediciting composite behaviour. I wanted to know if it is possible to have step 1 as STATIC IMPLICIT and step 2 as DYNAMIC EXPLICIT in a single input file? Please Advice. If this is not possible, what are other ways of doing the same thing.
>
> Your help will be much appreciated.
>
> Thank you
>
> Maajid
>
> ------------ --------- --------- ------
>
> Community email addresses:
> Post message: Abaqus@yahoogroups. com
> Subscribe: Abaqus-subscribe@ yahoogroups. com
> Unsubscribe: Abaqus-unsubscribe@ yahoogroups. com
> List owner: Abaqus-owner@ yahoogroups. com
>
> Shortcut URL to this page:
> http://groups. yahoo.com/ group/AbaqusYaho o! Groups Links
>
> -- Disclaimer ------------ --------- --------- ------
> Ce message ainsi que les eventuelles pieces jointes constituent une correspondance privee et confidentielle a l'attention exclusive du destinataire designe ci-dessus. Si vous n'etes pas le destinataire du present message ou une personne susceptible de pouvoir le lui delivrer, il vous est signifie que toute divulgation, distribution ou copie de cette transmission est strictement interdite. Si vous avez recu ce message par erreur, nous vous remercions d'en informer l'expediteur par telephone ou de lui retourner le present message, puis d'effacer immediatement ce message de votre systeme.
> ***
> This e-mail and any attachments is a confidential correspondence intended only for use of the individual or entity named above. If you are not the intended recipient or the agent responsible for delivering the message to the intended recipient, you are hereby notified that any disclosure, distribution or copying of this communication is strictly prohibited. If you have received this communication in error, please notify the sender by phone or by replying this message, and then delete this message from your system.
>
>
>
>
>
>
>
>
>
>
>
>
>
>
>
>
>
>
> [Non-text portions of this message have been removed]
>

Re: modelling of coating

2009-11-06T09:55:07Z

Try changing your unit system to millimeters.

Regards,

Dave

-------------------------
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

bin song wrote:

>
>
> Dear Dave
> I also face the same question. The coating' thickness can not be
> defined(less than 10exp(-6)m).
>
> --
> SONG Binbin
>
> -------------------------------
> Dept. of Phy
> USTB
> Beijing, 100083
> China
> --------------------------------------------
>
> --- 09年11月6日，周五, Dave Lindeman <ddlindeman@...
> <mailto:ddlindeman%40mmm.com>> 写道：
>
> 发件人: Dave Lindeman <ddlindeman@... <mailto:ddlindeman%40mmm.com>>
> 主题: Re: [Abaqus] modelling of coating
> 收件人: Abaqus@... <mailto:Abaqus%40yahoogroups.com>
> 日期: 2009年11月6日,周五,上午1:58
>
>
>
> In the Property module, define a shell section, then assign it to the
> appropriate faces of the solid part (after selecting "Assign Section",
> change the selection filter from "Regions" to "Skins", then select the
> faces).
>
> In the Mesh module you essentially do the same thing. After selecting
> "Assign Element Type", change the selection filter from "Regions" to
> "Skins", select the faces, and assign the appropriate shell or membrane
> element type.
>
> Regards,
>
> Dave
>
> ------------ --------- ----
> Dave Lindeman
> Lead Research Specialist
> 3M Company
> 3M Center 235-3F-08
> St. Paul, MN 55144
> 651-733-6383
>
> efe Eren wrote:
> >
> >
> > Dear Dave,
> >
> > thanks for the respond. As far as i know i couldn't set a coating
> > thickness if I use skin option. Am i wrong? another issue is the element
> > type. i couldn't find any data about it!
> >
> > Cheers,
> > Efe
> >
> > --- On Thu, 5/11/09, Dave Lindeman <ddlindeman@mmm. com
> > <mailto:ddlindeman% 40mmm.com> > wrote:
> >
> > > From: Dave Lindeman <ddlindeman@mmm. com <mailto:ddlindeman%
> 40mmm.com> >
> > > Subject: Re: [Abaqus] modelling of coating
> > > To: Abaqus@yahoogroups. com <mailto:Abaqus% 40yahoogroups. com>
> > > Date: Thursday, 5 November, 2009, 4:30 PM
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > > Normally you would just cover the exterior faces
> > > of the solid elements
> > >
> > > with shell elements. In CAE you can do this in the
> > > Property module
> > >
> > > (Special->Skin- >Create.. .). The skin can be
> > > assigned its own
> > >
> > > properties, thickness, etc.
> > >
> > >
> > >
> > > Regards,
> > >
> > > Dave
> > >
> > >
> > >
> > > ------------ --------- ----
> > >
> > > Dave Lindeman
> > >
> > > Lead Research Specialist
> > >
> > > 3M Company
> > >
> > > 3M Center 235-3F-08
> > >
> > > St. Paul, MN 55144
> > >
> > > 651-733-6383
> > >
> > >
> > >
> > > efe Eren wrote:
> > >
> > > >
> > >
> > > >
> > >
> > > > Dear All,
> > >
> > > >
> > >
> > > > I've asked this question before, but I
> > > couldn'y get any respond. there
> > >
> > > > might be an error in the mailing system, so i would
> > > like to send it again.
> > >
> > > > I have a modelling problem and i couldn't find a
> > > solution for it. I need
> > >
> > > > your sugesstions.
> > >
> > > >
> > >
> > > > I have a part which is coated. the properties of
> > > substrate and coating
> > >
> > > > materials are rather different than each other. how i
> > > should do my model?
> > >
> > > >
> > >
> > > > a) modelling as one part and assign the properties of
> > > coating material
> > >
> > > > to whole part.
> > >
> > > >
> > >
> > > > b) modelling separately (using partition or modeling
> > > one on top of other).
> > >
> > > >
> > >
> > > > First I thought model A, because the coating material
> > > defines the
> > >
> > > > surface interactions! on the other hand the mechanical
> > > respond of the
> > >
> > > > material would be different! The second one is the
> > > ideal one, but I've
> > >
> > > > faced with very very small time increment due to very
> > > thin coating part.
> > >
> > > > what should I do? is there another way or trick for
> > > this kind of problem?
> > >
> > > >
> > >
> > > > please help me!
> > >
> > > > Thanks in advance
> > >
> > > >
> > >
> > > > Efe Eren
> > >
> > > >
> > >
> > > > is there another way? I'll be appreciated if
> > > anyone can help me.
> > >
> > > >
> > >
> > > > Regards,
> > >
> > > > Efe
> > >
> > > >
> > >
> > > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> > >
> >
> >
>
> __________________________________________________________
> 好玩贺卡等你发，邮箱贺卡全新上线！
> http://card.mail.cn.yahoo.com/ <http://card.mail.cn.yahoo.com/>
>
> [Non-text portions of this message have been removed]
>
>

Re: Parametric study using python with UMAT

2009-11-06T07:18:17Z

Sorry Guys,

as it looks like the name of my VUMAT-file did not go well. Changed the name and now it seems to work.

Thanks you all
Fabian

Hi Frank,
Thank you for your answer!

I now defined my script.psf as follows:

# create the parametric study
aStudy=ParStudy (par='load_x', name='job1', directory=ON)

# define the parameter
aStudy.define(DISCRETE, par='load_x', domain=(0.5, 2.))

# sample the parameter
aStudy.sample(NUMBER, par='load_x', number=1)

aStudy.combine(MESH)

# generate analysis data
aStudy.generate(template='job1')

# execute all analysis jobs sequentially
aStudy.execute(ALL,execOptions='user=''vumat_orth.for')

However, if I run it wit the command 'abaqus script=script.psf' there is an ERROR saying that my VUMAT-file can't be found. But it is in the working directory!

Cheers
Fabian

Frank Richter-2 wrote:

Here is a template for your filename.psf with hexp being varied:

parst = ParStudy(par=('hexp'), name='filename',directory=ON)

parst.define(DISCRETE, par='hexp',domain=(-5,-10,-15))
parst.sample(REFERENCE, par='hexp', reference=1, interval=1, numSymPairs=1)

parst.combine(MESH)

parst.generate(template='filename')

parst.execute(ALL,execOptions='user=filename.for')

Frank

Extracting an element set

2009-11-06T04:21:04Z

Dear All,

I have a question please,

If a have created an element set in a CAE model to be analyzed and this model has been run with no problem and I got its ODB file. Is it possible to take the geometry of this element set to be as a part for a new model?

Sorry for bothering you and waiting for your kind reply

best regards,

khamis Essa

Khamis Essa
PhD Research Engineer
School of Mechanical Engineering
University of Birmingham
Birmingham B15 2TT
Mobile: +44 (0) 7727804354

[Non-text portions of this message have been removed]

buckling

2009-11-06T00:39:41Z

hi all,

I am doing bucking analsis of a assemby component.

I want to check the it for individual component.

As the loading and boundary conditions will vary if i consider the individual componet than whole assembly and its bit difficult to do that also.

Is it possible to check the buckling load for individual components by doing the analysis on the whole assembly?

thanks

sagar

Keep up with people you care about with Yahoo! India Mail. Learn how. http://in.overview.mail.yahoo.com/connectmore

[Non-text portions of this message have been removed]

Re: Parametric study using python with UMAT

2009-11-06T00:19:25Z

Hello,

you start your inp-file with

*PARAMETER
hexp = -5

Whenever this value is referred to in the inp-file, you need to put it into parentheses like <hexp>. The psf-file starts a sequence of simulations wherein hexp is replaced with the values given in the list.

See the User's Manual chapter on 'parametric studies'.

Frank

-------- Original-Nachricht --------
> Datum: Thu, 5 Nov 2009 10:37:29 -0800 (PST)
> Von: fehrich <f.ehrich09@...>
> An: ABAQUS@...
> Betreff: Re: [ABAQUS] Parametric study using python with UMAT

>
> Hi Frank,
> Thank you for your answer!
> However, I could not fully follow the procedure...
>
> So I write a filename.psf where I define my parameter (hexp) and how it
> should be varied according to your template.
>
> But how does it relate to my input-file model.inp?
>
> Cheers
> Fabian
>
>
>
> Frank Richter-2 wrote:
> >
> >
> >
> > Here is a template for your filename.psf with hexp being varied:
> >
> > parst = ParStudy(par=('hexp'), name='filename',directory=ON)
> >
> > parst.define(DISCRETE, par='hexp',domain=(-5,-10,-15))
> > parst.sample(REFERENCE, par='hexp', reference=1, interval=1,
> > numSymPairs=1)
> >
> > parst.combine(MESH)
> >
> > parst.generate(template='filename')
> >
> > parst.execute(ALL,execOptions='user=filename.for')
> >
> >
> >
> > Frank
> >
> >
> >
> >
> >
> >
>
> --
> View this message in context:
> http://old.nabble.com/Parametric-study-using-python-with-UMAT-tp14127909p26217369.html
> Sent from the Abaqus Users mailing list archive at Nabble.com.
>

--
-----------------------------------------------------------------------
Frank Richter
Institute of Materials Science
Ruhr-Universitaet Bochum
Bochum
Germany

DSL-Preisknaller: DSL Komplettpakete von GMX schon für
16,99 Euro mtl.!* Hier klicken: http://portal.gmx.net/de/go/dsl02

Re: modelling of coating

2009-11-05T16:49:31Z

Dear Dave
I also face the same question. The coating' thickness can not be defined(less than 10exp(-6)m).

--
SONG Binbin

-------------------------------
Dept. of Phy
USTB
Beijing, 100083
China
--------------------------------------------

--- 09年11月6日，周五, Dave Lindeman <ddlindeman@...> 写道：

发件人: Dave Lindeman <ddlindeman@...>
主题: Re: [Abaqus] modelling of coating
收件人: Abaqus@...
日期: 2009年11月6日,周五,上午1:58

In the Property module, define a shell section, then assign it to the
appropriate faces of the solid part (after selecting "Assign Section",
change the selection filter from "Regions" to "Skins", then select the
faces).

In the Mesh module you essentially do the same thing. After selecting
"Assign Element Type", change the selection filter from "Regions" to
"Skins", select the faces, and assign the appropriate shell or membrane
element type.

Regards,

Dave

------------ --------- ----
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

efe Eren wrote:

>
>
> Dear Dave,
>
> thanks for the respond. As far as i know i couldn't set a coating
> thickness if I use skin option. Am i wrong? another issue is the element
> type. i couldn't find any data about it!
>
> Cheers,
> Efe
>
> --- On Thu, 5/11/09, Dave Lindeman <ddlindeman@mmm. com
> <mailto:ddlindeman% 40mmm.com> > wrote:
>
> > From: Dave Lindeman <ddlindeman@mmm. com <mailto:ddlindeman% 40mmm.com> >
> > Subject: Re: [Abaqus] modelling of coating
> > To: Abaqus@yahoogroups. com <mailto:Abaqus% 40yahoogroups. com>
> > Date: Thursday, 5 November, 2009, 4:30 PM
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> > Normally you would just cover the exterior faces
> > of the solid elements
> >
> > with shell elements. In CAE you can do this in the
> > Property module
> >
> > (Special->Skin- >Create.. .). The skin can be
> > assigned its own
> >
> > properties, thickness, etc.
> >
> >
> >
> > Regards,
> >
> > Dave
> >
> >
> >
> > ------------ --------- ----
> >
> > Dave Lindeman
> >
> > Lead Research Specialist
> >
> > 3M Company
> >
> > 3M Center 235-3F-08
> >
> > St. Paul, MN 55144
> >
> > 651-733-6383
> >
> >
> >
> > efe Eren wrote:
> >
> > >
> >
> > >
> >
> > > Dear All,
> >
> > >
> >
> > > I've asked this question before, but I
> > couldn'y get any respond. there
> >
> > > might be an error in the mailing system, so i would
> > like to send it again.
> >
> > > I have a modelling problem and i couldn't find a
> > solution for it. I need
> >
> > > your sugesstions.
> >
> > >
> >
> > > I have a part which is coated. the properties of
> > substrate and coating
> >
> > > materials are rather different than each other. how i
> > should do my model?
> >
> > >
> >
> > > a) modelling as one part and assign the properties of
> > coating material
> >
> > > to whole part.
> >
> > >
> >
> > > b) modelling separately (using partition or modeling
> > one on top of other).
> >
> > >
> >
> > > First I thought model A, because the coating material
> > defines the
> >
> > > surface interactions! on the other hand the mechanical
> > respond of the
> >
> > > material would be different! The second one is the
> > ideal one, but I've
> >
> > > faced with very very small time increment due to very
> > thin coating part.
> >
> > > what should I do? is there another way or trick for
> > this kind of problem?
> >
> > >
> >
> > > please help me!
> >
> > > Thanks in advance
> >
> > >
> >
> > > Efe Eren
> >
> > >
> >
> > > is there another way? I'll be appreciated if
> > anyone can help me.
> >
> > >
> >
> > > Regards,
> >
> > > Efe
> >
> > >
> >
> > >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
>
>

___________________________________________________________
好玩贺卡等你发，邮箱贺卡全新上线！
http://card.mail.cn.yahoo.com/

[Non-text portions of this message have been removed]

RE: Vicoelastic simulation using DMA data

2009-11-05T13:56:56Z

Following on from Narinder's suggestion, look for the subheading "Frequency-dependent test data". Abaqus can accept your storage and loss modulus (vs. frequency) data and calculates the terms of a Prony series to represent the viscoelastic response for you.
DLL

Danny L. Levine, Ph.D., P.E.
Principal Engineer
Zimmer, Inc.
(574)372-4669 - office
(574)298-4799 - cell
//http:www.zimmer.com
________________________________
From: Abaqus@... [mailto:Abaqus@...] On Behalf Of Narinder Singh Khattra
Sent: Thursday, November 05, 2009 8:39 AM
To: Abaqus@...
Subject: Re: [Abaqus] Vicoelastic simulation using DMA data

Hi Adel,

I hope you have seen

"*Viscoelastic" in ABAQUS Keywords Reference Manual and

"Time domain viscoelasticity" in ABAQUS Analysis User's Manual

-NS

---- Original message ----

>Date: Wed, 04 Nov 2009 20:56:00 -0000
>From: Abaqus@...<mailto:Abaqus%40yahoogroups.com> (on behalf of "adel a" <abdelghaffar_adel@...<mailto:abdelghaffar_adel%40yahoo.com>>)
>Subject: [Abaqus] Vicoelastic simulation using DMA data
>To: Abaqus@...<mailto:Abaqus%40yahoogroups.com>
>
>
>
> Hi everybody
> please could any one tell me how to implement data from DMA experiment: storage modulus,
> loss modulus, as function of ferquency
> in the material definition of an Abaqus simulation.
>
> Thank you in advance.....
>
> Adel
>
>

[Non-text portions of this message have been removed]

6-node elements with hourglass control and modified displacement

2009-11-05T13:28:01Z

Hello Everyone,

My name is Sherif Akl, a PhD student working with ABAQUS on solving
geotechnical engineering problems. I was simulating Triaxial experiments
using CAX6MP. The problem is I can't find anywhere in the manual the
interpolation functions used for these elements. Apparently, they
introduced new features to the formulation to control Hour Glassing. The
manual is not clear on that.

If anybody used them or has an idea about that type of formulation.
Please point me in the right direction.

Sherif

Re: Changing material property over coordinates

2009-11-05T12:02:20Z

You should be able to define your elastic modulus values as a tabular
function of a field variable (set the number of field variables to "1"
when defining an elastic material in the "Edit Material" dialog box).
In this case, the field variable value will correspond to your
Y-coordinate. Unfortunately, ABAQUS/CAE doesn't currently support the
definition of predefined field variables (even though it has tools to
define discrete and analytical fields which can be used in interaction
and load definitions). So, you'll need to edit the input file to add a
*INITIAL CONDITIONS,TYPE=FIELD,VARIABLE=1 section and/or a
*FIELD,VARIABLE=1 section to actually define the field variable values.
Alternatively, you can use the UFIELD subroutine (this might actually
be easier, since the coordinates of the nodes are passed into the
subroutine, and all you'll have to do is set FIELD(NSECPT,1) = COORDS(2)).

Regards,
Dave

-------------------------
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

S.M.Ali Tasaloti wrote:

>
>
> Hello to all,
> Maybe my question is easy but I didn't find any answer for it. I want
> for example to change the young modulus of material linearly over
> y-coordinate of the 2D model. My specific question is about clay
> plasticity which I want to change the intercept over y-coordinate.
> How can I do so?
>
> Your help is kindly appreciatd.
>
> tnx
>
> S.M.Ali Tasalloti
>
>

Re: Determining Stabilization Damping factor + Rikz analysis problems

2009-11-05T11:06:27Z

1) I'm note sure that you can calibrate the stabilization damping factor
-- it may be problem dependent. However, if establish correlation to
existing experimental data, and the energy associated with the
stabilization is small compared to the other energies in the system,
then, for SIMILAR problems, you should have increased confidence that
the stabilization damping value will give reasonable results (but you
must always check the energy).

4) Use *DYNAMIC rather than *STATIC (or *VISCO).

Regards,

Dave

-------------------------
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

Ihab El Aghoury wrote:

>
>
> Hi Dave,
>
> Thank you for your reply. It is a static loading for a simple beam at
> two points till failure (a very simple test). The actual test at failure
> has a little bit of local buckling in the compression flange (at the
> late stages of the test).
>
> 1- My problem is how to calibrate to this damping if I don't have
> experimental results (I'm 95% sure of the experimental results).
>
> 2- When I did the Static analysis WITHOUT stabilization + NL-GEOM ON ->
> gave nearly the same behaviour as : RIKS analysis WITHOUT NL-GEOM which
> both of them give a higher load than the Experimental.
>
> 3- If I want to capture the post failure Load reduction part, I need
> RIKS analysis, which doesn't complete with NL-GEOM ON. How could I
> increase the number of trials per increment. Note that RIKS analysis
> doesn't have any stabilization options.
>
> 4- How to do a slow transient analysis, what do you mean by it ?
>
> Please help me to understand the above,
>
> Thank you so much
>
> Yours,
>
> Ihab El-Aghoury
>
> Research and Teaching Assistant
> Department of Building, Civil & Environmental Engineering
> Concordia University
> 1515 Rue Ste-Catherine West, EV 11.111
> Montreal, Quebec, Canada H3G 2W1
> Tel: 514-848-2424 Ext. 7198
> Cellular: 514-996-2919
>
> ____________ _________ _________ __
> From: Dave Lindeman <ddlindeman@mmm. com>
> To: Abaqus@yahoogroups. com
> Sent: Fri, October 16, 2009 11:48:05 AM
> Subject: Re: [Abaqus] Determining Stabilization Damping factor + Rikz
> analysis problems
>
> Please explain the test in a little more detail. Does the beam exceed a
> buckling load, or does it just experience plastic deformation? If the
> beam only experiences plastic deformation, then you objective should be
> to get the simulation to run WITHOUT stabilization. If it does buckle,
> then stabilization (or the Riks method) may be necessary. An
> alternative might be to run the simulation as a slow transient.
>
> Regards,
>
> Dave
>
> ------------ --------- ----
> Dave Lindeman
> Lead Research Specialist
> 3M Company
> 3M Center 235-3F-08
> St. Paul, MN 55144
> 651-733-6383
>
> ihab_elaghoury wrote:
> >
> >
> > Hi everybody,
> >
> > I've modeled a simple steel beam that I've tested experimentally with
> > 4-point loading. I've inputted the material exactly as the tested
> > coupons. I've included Geometrical non-linearity. I'm measuring the
> > response (Load-deflection and Load-Strains) . Own weight is NOT
> included.
> > I ran the analysis using two different methods :
> >
> > 1- GENERAL STATIC:
> > ------------ ------
> > I've run the analysis using automatic stabilization using various
> > damping factors until I reached a value of 0.0011 (without adaptive
> > Stabilization) that gave nearly the same response as experimental (In
> > the plastic part). Changing the damping factor always SIGNIFICANTLY
> > changed the Plastic (non-linear) part of the response.
> >
> > * So , I was wondering how would I accurately determine the damping
> > factors of any other model if I don't have any experimental data to
> > verify it and calibrate it.
> >
> > ============ ========= ========= ========= ========= ========= ======
> >
> > 2- STATIC RIKZ :
> > ------------ ----
> > I've run the analysis with very small arc length and minimum increment,
> > but always the analysis stops (for many trials) at a load of about half
> > the failure load. I don't know how to fix it. When I removed Geometrical
> > non-linearity, the analysis continues and gives a higher response than
> > experimental. There are no other calibration options in the RIKZ
> analysis.
> >
> > * So , I was wondering why is the big difference between including
> > Geometrical non-linearity and not including it in Rikz analysis
> >
> > In general, I need to know if my analysis is going in the right
> > direction or not.
> >
> > Thank you so much...
> >
> >
>
> ____________ _________ _________ _________ _________ _________ _
> Be smarter than spam. See how smart SpamGuard is at giving junk email
> the boot with the All-new Yahoo! Mail. Click on Options in Mail and
> switch to New Mail today or register for free at http://mail. yahoo.ca
>
> [Non-text portions of this message have been removed]
>
> __________________________________________________________
> Yahoo! Canada Toolbar: Search from anywhere on the web, and bookmark
> your favourite sites. Download it now
> http://ca.toolbar.yahoo.com. <http://ca.toolbar.yahoo.com.>
>
> [Non-text portions of this message have been removed]
>
>

Re: Parametric study using python with UMAT

2009-11-05T10:37:26Z

Hi Frank,
Thank you for your answer!

I now defined my script.psf as follows:

# create the parametric study
aStudy=ParStudy (par='load_x', name='job1', directory=ON)

# define the parameter
aStudy.define(DISCRETE, par='load_x', domain=(0.5, 2.))

# sample the parameter
aStudy.sample(NUMBER, par='load_x', number=1)

aStudy.combine(MESH)

# generate analysis data
aStudy.generate(template='job1')

# execute all analysis jobs sequentially
aStudy.execute(ALL,execOptions='user=''vumat_orth.for')

However, if I run it wit the command 'abaqus script=script.psf' there is an ERROR saying that my VUMAT-file can't be found. But it is in the working directory!

Cheers
Fabian

Frank Richter-2 wrote:

Here is a template for your filename.psf with hexp being varied:

parst = ParStudy(par=('hexp'), name='filename',directory=ON)

parst.define(DISCRETE, par='hexp',domain=(-5,-10,-15))
parst.sample(REFERENCE, par='hexp', reference=1, interval=1, numSymPairs=1)

parst.combine(MESH)

parst.generate(template='filename')

parst.execute(ALL,execOptions='user=filename.for')

Frank

RE: Vicoelastic simulation using DMA data

2009-11-05T10:32:53Z

Also check out Joergen Bergstrom's website PolymerFem for a discussion on converting storage and loss modulus data into a Prony Series approximation for FEA modeling of viscoelastic materials.
http://polymerfem.com/forums/showthread.php?t=91

DLL

Danny L. Levine, Ph.D., P.E.
Principal Engineer
Zimmer, Inc.
(574)372-4669 - office
(574)298-4799 - cell
//http:www.zimmer.com
________________________________
From: Abaqus@... [mailto:Abaqus@...] On Behalf Of Narinder Singh Khattra
Sent: Thursday, November 05, 2009 8:39 AM
To: Abaqus@...
Subject: Re: [Abaqus] Vicoelastic simulation using DMA data

Hi Adel,

I hope you have seen

"*Viscoelastic" in ABAQUS Keywords Reference Manual and

"Time domain viscoelasticity" in ABAQUS Analysis User's Manual

-NS

---- Original message ----

[Non-text portions of this message have been removed]

Re: modelling of coating

2009-11-05T09:58:39Z

In the Property module, define a shell section, then assign it to the
appropriate faces of the solid part (after selecting "Assign Section",
change the selection filter from "Regions" to "Skins", then select the
faces).

In the Mesh module you essentially do the same thing. After selecting
"Assign Element Type", change the selection filter from "Regions" to
"Skins", select the faces, and assign the appropriate shell or membrane
element type.

Regards,

Dave

-------------------------
Dave Lindeman
Lead Research Specialist
3M Company
3M Center 235-3F-08
St. Paul, MN 55144
651-733-6383

efe Eren wrote:

>
>
> Dear Dave,
>
> thanks for the respond. As far as i know i couldn't set a coating
> thickness if I use skin option. Am i wrong? another issue is the element
> type. i couldn't find any data about it!
>
> Cheers,
> Efe
>
> --- On Thu, 5/11/09, Dave Lindeman <ddlindeman@...
> <mailto:ddlindeman%40mmm.com>> wrote:
>
> > From: Dave Lindeman <ddlindeman@... <mailto:ddlindeman%40mmm.com>>
> > Subject: Re: [Abaqus] modelling of coating
> > To: Abaqus@... <mailto:Abaqus%40yahoogroups.com>
> > Date: Thursday, 5 November, 2009, 4:30 PM
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> > Normally you would just cover the exterior faces
> > of the solid elements
> >
> > with shell elements. In CAE you can do this in the
> > Property module
> >
> > (Special->Skin- >Create.. .). The skin can be
> > assigned its own
> >
> > properties, thickness, etc.
> >
> >
> >
> > Regards,
> >
> > Dave
> >
> >
> >
> > ------------ --------- ----
> >
> > Dave Lindeman
> >
> > Lead Research Specialist
> >
> > 3M Company
> >
> > 3M Center 235-3F-08
> >
> > St. Paul, MN 55144
> >
> > 651-733-6383
> >
> >
> >
> > efe Eren wrote:
> >
> > >
> >
> > >
> >
> > > Dear All,
> >
> > >
> >
> > > I've asked this question before, but I
> > couldn'y get any respond. there
> >
> > > might be an error in the mailing system, so i would
> > like to send it again.
> >
> > > I have a modelling problem and i couldn't find a
> > solution for it. I need
> >
> > > your sugesstions.
> >
> > >
> >
> > > I have a part which is coated. the properties of
> > substrate and coating
> >
> > > materials are rather different than each other. how i
> > should do my model?
> >
> > >
> >
> > > a) modelling as one part and assign the properties of
> > coating material
> >
> > > to whole part.
> >
> > >
> >
> > > b) modelling separately (using partition or modeling
> > one on top of other).
> >
> > >
> >
> > > First I thought model A, because the coating material
> > defines the
> >
> > > surface interactions! on the other hand the mechanical
> > respond of the
> >
> > > material would be different! The second one is the
> > ideal one, but I've
> >
> > > faced with very very small time increment due to very
> > thin coating part.
> >
> > > what should I do? is there another way or trick for
> > this kind of problem?
> >
> > >
> >
> > > please help me!
> >
> > > Thanks in advance
> >
> > >
> >
> > > Efe Eren
> >
> > >
> >
> > > is there another way? I'll be appreciated if
> > anyone can help me.
> >
> > >
> >
> > > Regards,
> >
> > > Efe
> >
> > >
> >
> > >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
> >
>
>