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-   -   Periodic compressor simulation (http://www.cfd-online.com/Forums/cfx/72755-periodic-compressor-simulation.html)

Attesz February 17, 2010 07:01

Periodic compressor simulation
 
Hi all,

I'm doing a centrifugal compressor simulation. To speed up the simulation, I want to use only a blade passage instead of the whole geometry. To get this, I have to slice the geom to a periodic piece. What is the recommend way?
1. Slice between the blades, so I get a geometry bounded by periodic boundary conditions with a blade in the middle, or
2. Slice at the centroid of the blade, so I get a clear blade passage, bounded by blade walls.

I found examples for the type 1., but the second one seems to be good too.

Thanks for any advice,
Attesz

puga February 18, 2010 14:43

I'm relatively new to CFD, but would suggest the first option. Let me put it this way: a periodic boundary is only going to increase the local complexity of the problem. That being said, would you rather have the possible error from this near the object of interest (the airfoil), or away? I'd go with the latter. It seems to be the general practice from what I've seen.

Alternatively, you could do a 2-airfoil passage and get the best of both worlds, but sacrifice run some run time.

ghorrocks February 18, 2010 16:58

The boundary layer on the blade is often critical to accurate models. To get a good boundary layer you need a good mesh with no interuptions and so it is usual to move anything boundaries away from these areas. That is why option 1 is normal chosen. But if the periodic boundary is 1 to 1 option 2 can work. If it is a GGI that is not recommended.

Attesz February 23, 2010 05:49

Hi,

thanks to all, I will do the 1. type, because the periodic surface mesh is not 1:1, and the compressor has tip gap. Fortunately, I could slice the geometry in DesingModeller (I couldn't believe in this before) so this way can work.

Thanks again for the answers,
Attesz

Attesz March 3, 2010 05:42

transient rotor-stator interface
 
Hi all,
i've done with the geometry, It works fine in steady state simulation (with wrong results unfortunately). We want to do a transient simulation, in first step with frozen rotor interfaces, and then with the transient rotor-stator. My question is: can CFX use well the transient rotor-stator interface with periodic geometry? Because here the domain will be physically rotated...

Thank you,
Attesz

ghorrocks March 3, 2010 05:54

You cannot use frozen rotor in a transient simulation. It is only valid for steady state flows.

You can use TRS interfaces with periodicity.

Attesz March 3, 2010 06:27

Ok, good news, thanks!

Regards,
Attesz

Attesz March 24, 2010 10:16

1 Attachment(s)
Hi all,
Glenn wrote that I cannot use frozen rotor, but in transient simulation, I can set the interfaces to Frozen Rotor, it's allowed. But, it's not physically valid, mostly when the periodicity in the rotor and stator has not the same angle. I think, stage option is better. But, if I use huge difference between the periodicity angles or pitch, I can get wrong results with stage also? Is there a recommened upper/lower value for pitch change? In my case the pitch change between stator& rotor is 2. Is it more suitable to use 2 blade passages from impleller to get pitch change to 1? Using this means more cells and computational time.

Thanks for any advice,
Attesz

Attesz October 19, 2010 08:36

1 Attachment(s)
Hi all,

i have a question in the simulation project of this thread, but it can be a general one as well.
So I'm running a steady simulation on a centrifugal compressor-diffuser stage, and when I increase the pressure ratio, the massflows converge hardly. Also the RMS residuals are increasing, while the MAX residuals are high from the beginning. I use a fine, unstructured tetra mesh, SST k-w model, 120deg periodic geometry with frozen rotor interfaces. The increase in RMS occurs under the operational point, so it is far from surge too. the outlet boundary condition is average static pressure. Now, i've switched to mass flow outlet, and the residuals are going down, as you can see on the picture. Why is this happened?

An other question, because of the increased Timescale Factor, the convergence can be poor when i would use lower factors? Is there any upper limit for that factor? Currently i'm using 50 and 100, but there is no significant difference in between.

Attachment 5018

Thanks,
Attesz

ghorrocks October 19, 2010 17:42

http://www.cfd-online.com/Wiki/Ansys...gence_criteria


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