This article will appear in Journal of ASTM International.  I hope you find it useful.

Xiao-Yan Gong, President, medical implant mechanics LLC

www.medicalimplantmech.com

Red Cedar Technology recently released its latest version of their design optimization and process automation software, HEEDS v5.3. It has direct interfaces to Abaqus, LS-DYNA, and other tools.

Check out the press release, or go read about the new features.

More information about residual stress tester

The residual stress in a metal do not depend on its hardness, but from the module of elasticity or Young module and from its chemical composition (density).
The hardness of a metal indicates its ability to absorb energy elastic, plastic or kinetic energy, but through it not possible to determine the value of residual stress. In a metal with the same hardness we will have a different values of this stress. Therefore, the problem will be to measure the values that vary so exactly proportional to the residual stress values in a given metal.
The residual stresses tend to equilibrate themselves in the surface of the material.

Hello Friends,

I am working with abaqus since last year,

I am facing the problem in assigning the hardness property to the material in Abaqus.

If some one knows ,how to Assign a hardness in Abaqus Please let me Know.

Hi,

Can anybody throw some light on the wear coupling characteristics between SS347 and 17-4 PH, as well as between Phosphor Bronze and 17-4 PH Steel?

It will be helpful if you could refer to some literature where I can learn about Wear Coupling Characteristics...

Thank You,

Navanee

The following is taken from the book Concepts and applications of Finite element methods by Cook, Malkus and Plesha.

 For bifurcation buckling, we have the following eigenvalue problem:

(K+Lambda Ksigma)delta d= 0 

Hi to the community !

I would like to ask if anyone have some experience with stochastic finite elements in an industrial context ?

Would you know some software (free or commercial) package for stochastic finite elements ?

Why do I have the feeling that sfem methods which look to be very promising aren't used much in practice ? Am I wrong when I say that ?

Thank you very much for any help about that !

Thomas Laverne

Hello,

I would like to know how contact elements are different from " general "ie non contact finite elements.

Also I would like to know how Lagrange multiplier method is used in contcat analysis.

My understanding of the Lagrange multiplier is like this: when we have to impose a constraint equation

[C][D]=[Q] as constraint between DOFs, we incude a term Y*{[[C][D]-[Q]} where Y is the Lagrange multiplier ,in the potential energy functional and minimize the functional  to get the algebraic equations.

I am trying to learn non linear FEA ( Newton Raphson method)and this is what my understanding is. Kindly advise if you think my understanding is correct.

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Hi, everyone

I am a student. I am  dealing with a failure problem of brittle spheres. These have a lot of flaws inside.I did some compression tests. Single spheres are crushed by a pair of parallel plates. I got the crush load distribution (in terms of critical contact force). 

My question is:

is there a failure criterion/model which relates to load(critical contact force), Youngs moduli and Poisson ratios of shpere and plates, radius and friction coefficient?

 Unfortranitaly, I can't get the friction coefficient between plate and sphere which influences the surface stress of spheres significantly as shown in ABAQUS simulation.

 Both theoretical and empirical models are welcome.  

Dear Sir/Madam,

Interlaminar stresses in Composites

I have modelled Plain Stress problem in hypermesh(Input deck is created in Hypermesh to solve in Abaqus).Layup sequence is [0/90/90/0], am getting the Stresses( σ11, σ22, σ12) in top and bottom layers only, but unable to get the stresses at each Interface, If any one knows how to write the code, please reply back.

My doubt is in transient dynamic analysis.

take a simple model of 40*2*1 m dimensions.Applying brick45 material. with e=2.069e11N/m2

poissons ratio= .3

density= 7830kg/m3

first performing modal analysis with just arresting displacements in 1 side in subspace method and getting 10 sets of frequencies..

then performing transient dynamic analysis in mode superposition method with dynamic loads.and solve it

i can get value of the stress or displacement at each node and i can plot a graph for time vs displacement or stress at that node by using time history post processor.

what i need is

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Respected imehanicians!
                      I am a tackling an important problem about the behavior of concrete tied arch. Each concrete arch rests on two steel I-beams. The steel I-beams are supported at their ends. They are connected at various locations along their length by tie rods. A picture is worth 1000 words  basic figure.pdf.

I want to simulate mold filling of a bar mold with a semisolid alloy by means of FLOW3D cfd package. but there are some problem. for example when I input a file I encounter an error like "level   1 error in subroutine rdstl: level   1 error in subroutine rdstl"in preprocessor. what can I do? does my .stl file have any faults?

other problem with another project is that when i want to solve the problem I encounter an error like "convective flux exceeded stability limit".repeatedly. is my meshing insufficient? how can I solve that too?

any useful guide is appreciated.

thanks a lot. 

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The Shore A and D hardness tests are widely used by the rubber industry.  However, I'm not sure what practical use these numbers can be put to during design.  My current feeling is that Shore hardness numbers can at best give you a feel for the texture of the rubber - a Shore A value of 5 = gummy bear texture, Shore A = 40 implies erasure texture etc.

Can someone explain how Shore hardness values can be used in the design of mechanical components made of rubber?

Thanks in advance,

Biswajit 

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