CFD Online Logo CFD Online URL
www.cfd-online.com
[Sponsors]
Home > Forums > CFX

SSG Reynolds Stress Turbulent Source on Boundary

Register Blogs Members List Search Today's Posts Mark Forums Read

Reply
 
LinkBack Thread Tools Display Modes
Old   September 10, 2012, 19:31
Default SSG Reynolds Stress Turbulent Source on Boundary
  #1
New Member
 
Susan Tully
Join Date: Jul 2012
Posts: 15
Rep Power: 4
st268 is on a distinguished road
Hello,

I have been trying to input a turbulent boundary source into my model. Very simply I have two cubic fluid domains that share one side as an interface. Water flows in one side of one cube at 1/4m/s through the interface and out the far-side of other cube, such the the inlet and outlet are parallel. I am using the SSG Reynolds Stress Model and have to define the stress tensor coefficients and a diffusion rate.

I want my source to roughly give a 10% turbulent intensity (I). From reading up on the solver theory guide I have been using the following to calculate k, epsilon and uiuj values:

k = (3/2) (U(freestream)*I)^2 units [m^2s^-2]

uiuj = (2/3)k for i=j, 0 otherwise units [m^2s^-2]

epsilon = Rho*C*(k^2/dviscosity*viscosityRatio) units [kg m^-1 s^-3]

where C is 0.1 and viscosityRatio is 10

Then when I come to input these into CFX-Pre the units required (for a total source) are:

uiuj [kg m^2 s^-3] so I assume I have to multiply my k value by my mass flow rate to account for the missing [kg/s] right?

epsilon [kg m^2 s^-4]. Here the missing units are [m^3/s], I assume that its now volume flow rate I have to multiply my epsilon values by since the density has already been taken into account in my original equation?

When I do my calculations assuming:
I=0.1,
C=0.1,
dviscosity=1.117e-6[m^2s^-1],
viscosityRatio=10, U=1.4[m/s],
total mass flow rate =5.5e4 [kg/s],
volume flow rate = 53.76 [m^3/s]

I end up with the following (in the form required by CFX-Pre):

uiui = 1078 [kg m^2 s^-3]

epsilon = 409077 [kg m^2 s^-4]

This just seems wrong to me, is that dissipation rate not way too large?

When I run the simulation, either my solution diverges dramatically and the solver crashes or I see no change in my velocity flow field going through the interface.

Can anyone shed some light on the reason for this? Is it the way I have calculated my values above, or is it the turbulent domain settings for my two cubes? I have left the domain settings to default, should I be changing the epsilon coefficients for the domains too? My geometry is so simple (free slip walls all round, nothing obstructing flow) that any turbulence is very quickly dissipated, when I set the inlet to high turbulence (I=10%, dvRatio=100) then I still see the turbulence for a short distance from the inlet, I see nothing at my turbulent interface.

Any help would be greatly appreciated!

thanks

Susan

Last edited by st268; September 10, 2012 at 19:56.
st268 is offline   Reply With Quote

Old   September 10, 2012, 22:40
Default
  #2
Super Moderator
 
Glenn Horrocks
Join Date: Mar 2009
Location: Sydney, Australia
Posts: 10,646
Rep Power: 84
ghorrocks has a spectacular aura aboutghorrocks has a spectacular aura aboutghorrocks has a spectacular aura about
I do not have time to check your maths so I will leave that bit up to you.

But for the convergence difficulties, I recommend you start with a simpler model, maybe a 2-eqn turbulence model and see if that converges. If that is OK then go to RSM with simple default boundary conditions. This way you can tell whether the simulation itself has a problem, it is RSM or is your boundary conditions.

Be aware that RSM models are much harder to converge than 2-eqn turbulence models and are very sensitive to mesh quality.
ghorrocks is offline   Reply With Quote

Old   September 11, 2012, 03:24
Default
  #3
New Member
 
Susan Tully
Join Date: Jul 2012
Posts: 15
Rep Power: 4
st268 is on a distinguished road
I have already run through everything exactly as you said: using k-epsilon and it converges easily, witched to SsG with no turbulent interface and got a converged solution albeit after more iterations (as expected). I am looking at spatial/temporal pressure on a disk in turbulent flow so I need the SSG Reynolds Stress model to see the turbulence more clearly and am using a transient solution.

My question isnt about my arithmetic it is about the equations I have used and assumptions I have made about units. Even increasing my viscosity ratio to 100 I still get an eddy dissipation rate which is 10 times larger than my k value. I am asking if that seems physically correct as I see very little turbulence at my interface.

thanks

Susan
st268 is offline   Reply With Quote

Old   September 11, 2012, 07:24
Default
  #4
Super Moderator
 
Glenn Horrocks
Join Date: Mar 2009
Location: Sydney, Australia
Posts: 10,646
Rep Power: 84
ghorrocks has a spectacular aura aboutghorrocks has a spectacular aura aboutghorrocks has a spectacular aura about
The dissipation is frequently far higher than production - it just means the turbulence is being heavily damped in that area. This is a real effect.

Have a look at the production versus dissipation for the k-e and SSG runs in that area.
ghorrocks is offline   Reply With Quote

Reply

Thread Tools
Display Modes

Posting Rules
You may not post new threads
You may not post replies
You may not post attachments
You may not edit your posts

BB code is On
Smilies are On
[IMG] code is On
HTML code is Off
Trackbacks are On
Pingbacks are On
Refbacks are On


Similar Threads
Thread Thread Starter Forum Replies Last Post
swak4foam building problem GGerber OpenFOAM Installation 54 April 24, 2015 16:02
swak4Foam-groovyBC build problem zxj160 OpenFOAM 18 July 30, 2013 13:14
"parabolicVelocity" in OpenFoam 2.1.0 ? sawyer86 OpenFOAM Running, Solving & CFD 21 February 7, 2012 12:44
Version 15 on Mac OS X gschaider OpenFOAM Installation 120 December 2, 2009 11:23
Reynolds Stress Boundary Conditions tstorm FLUENT 0 July 27, 2009 14:44


All times are GMT -4. The time now is 06:44.