Today I finished my “Homework” for the NAFEMS Nonlinear Course (http://www.nafems.org/professional_development/nafems_training/training/el_nonlinear/) and I decided to write a post about this interesting exemple, the Hertz Contact !

## Hertz Contact: Description of the problem

This problems describes the behavior of a steel cylinder pressed into an aluminium block. Both materials are assumed as linear elastic materials and the cylinder is loaded by a load of F= 35kN in he Vertical direction.

Analytic solution of this problem is known for 2D plain strain and frictionless model.

## Results to be determined

The typical results we want to see are the peak contact stress, the contact radius and stress variation through depth under peak contact stress.

## Theoretical Results

I found a nice paper giving the theoretical solution for a 2D Plane Strain Problem Here.

The Maximum Contact Pressure is given by:

The contact Width 2a is given by:

For the given problem, the following results “should be” obtained:

## Random problems that I met solving the model

1- The Force of 35kN mentioned is a point load, so if the model used is 3D and the force is applied on the top edge of the cylinder, Force is actually lineic force and the value of the force should be defined as 35kN divided by the actual thickness (Special Thank to Johan Epingga for the tip…)

2- Using symmetry boundary condition is a must as it decreases by 2 the number of elements in the model, so this is especially helpful if you run the simulation in 3D…

3- Mesh should be really really good in the zone of contact to get correct results, so the best is to create manually the mesh using 2D meshing and size control and then extruding all that.

4- The assignment of the load is tricky if you assign it on the nodes. Best way in this case is to link the nodes with some rigid link to one unique node on which you apply the -35/2 kN loading (symmetry–>load is divided by 2)

5- Contact parameters are also tricky, midas NFX is using the penalty method for general contact, so you should keep in mind that the penetration will play a big influence on the results. I decided to set a contact tolerance of 0.001 mm to keep the penetration acceptable.

## My process to solve all that

#### Hypothesis

1- Theoretical solution is for 2D plain strain model, but it requires to use gap element is midas NFX, so I will solve it for a 3D Model.

2- I will general contact with penalty method and a contact tolerance of 0.01mm without friction (maybe i will try with friction too afterwards :) )

#### Model creation

1- Create the skeleton of the model by sketching the edges

2- Dividing edges in the right manner to apply size control

3- Meshing the 2D faces using manual map-meshing

4- Using Extrude mesh function to create 3D Mesh

#### Boundary conditions and loading

1- Symmetry BC is applied to the symmetric face…

2- Bottom of the block part is fixed

3- Load is applied as a point load of 17.5kN using rigid links to the nodes at the Top of the model

#### Contact

General contact with a contact tolerance of 0.001 mm applied to the surfaces in contact. The Master surface is the top surface of the block and the slave face is the bottom surface of the cylinder.

## Results

Here is what I got for the moment :

I am not sure the results are correct…let’s find why T_T

*You were right Tony, Nonlinear Analysis is not so straightforward…Hope at the end of the course I will get better results*

**Update (2014-11-10):**

I modified a bit the model by adding soft springs and making a better contact region. I realized also that the mesh shape had a great influence on the results and I made some better mesh:

Here is the stress distribution I got in the contact area:

And here is the curve:

It proves one thing: I got much better results than in the first try with lesser elements…

Now you can see how much model building is important in FEA Nonlinear Analysis…

Thanks for following up

I invite you to add your own results in the comments and discuss about it ! :)

Keith J. Orgeron, P.E. says

Cyprien, I enjoy reading your posts… and I too am blessed to be an engineer. Thanks for your efforts. Now, if I didn’t miss your mentioning this topic from your NAFEMS NL class, I recommend that you “discover” via the FEM (because you probably already know the answer empirically) the root cause and failure mechanism behind many contact stress failures, such as in gearing. Hints: 1) a linear contact solution is sufficient; 2) the solution is quite mesh-dependent; 3) case-hardening is a common solution. Keep up the good work! Regards, Keith

Cyprien says

Thank you very much Keith ! I am glad you liked the post. is a linear contact solution really sufficient? I guess I’ll have to think more about this problem…

Keith Orgeron says

Cyprien, officially, this is a change of state problem, requiring iterative solution of the stiffness matrix which is by definition, a nonlinear solution. So, your suspensions are correct. However, most FEA suppliers package a multi-body contact capability with a solution for linear materials and linear displacements and call it “linear contact”. So, as long as you use linear material properties and your displacements are in the realm of a linear solution, such a capability would suffice for Hertz contact. However, given you are set up to perform a full nonlinear analysis, I would recommend you go ahead with the assumptions mentioned and numerically “discover” the root cause and failure mode of bearing contact. All the best, Keith.

boussalia says

I would like to know how you have plot the contact stress graph versus x axix (mm) with workbench?

it’s urgent

best regards

Cyprien says

Check this article, Boussalia:

http://www.padtinc.com/blog/the-focus/making-charts-and-tables-in-ansys-mechanical

boussalia says

thanks for you cyprien

but i cant plot contact pression vs ax (mm) like you

i cant change time in axe x with the lenght of the contact area.

please show me How did you do?