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 Tudor Miron March 8, 2004 20:26

Hi All, I'm new to CFX so I have some dumb questions - sorry. I'm using CFX for automotive project - trying to design a good aero package for race car. I tryed my first solution and already have some problems: First I saved SolidWorks file as IGES and imported it in Build. I choused mm's for new database as I was told that this is the way to go with IGES files.

Solid created nicely. I went on to create the mesh – choused 5 for max edge length (mesh parameter), created Mesh Control and choused 1.5. Inflation parameter 5. For inflation boundary I choused model and flour as most important areas. Proximity set to 4. Created 3D and 2Dregions

Than I made a GTM file and went to Pre. Domain, than Car body itself – no slip, domain top, side and bottom walls – added to region and free slip. Front wall – Inlet: subsonic, normal speed 44.44 m^-1, Turbulence medium 5%. Outlet: subsonic, Average static pressure, 0 Pa. Symmetry plane – symmetry. Domain models: Air ideal gas, ref. pressure 1e05 Pa, no buoyant and stationary. Fluid models: Isothermal, 25C, SST, rest as default. Steady state Solver control: High resolution, Physical timescale 1s, RMS 0.0001, Dynamic control on Body Forces – averaging type Volume –weighted.

Went to solver and started run. Solver showed that mesh has

Total Number of Nodes = 176886 Total Number of Elements = 670227

Total Number of Tetrahedrons = 519362

Total Number of Prisms = 150865 Total Number of Faces = 47961 It solved with no probs and target convergence was achieved.

Than I went to Post and got very strange numbers

Lift -1.64Nm and drag 0.24Nm ….. that looked VERY wrong . This was a model of car with full length tunnel and pressure plot showed very good pressure drop under tunnel also in my wildest dreams I can't expect 0.24Nm of drag!

Also when I created a point to attach a streamline it all got strange – to fit in domain (15m long) I had to choose 0,02 0.001 0.15 ! I started to wonder what units is it….

Than I went back to builder and checked again geometry units – it was mm's. Than I tried to create a point with 1000 1000 1000 coordinates – could not see it. So to get within domain I had to make 50 50 50 !

So now I have a feeling that some how my model shrunk to very small thing….

I have to say here that I have limited time access to program – 2 hours a day – no more. So it's hard to study manual really carefully. Any advise will be highly appreciated.

If anybody has experience with modeling flow around car and correlated it to wind tunnel results please give me some advise on boundary conditions etc.

Thank you Ted

Sorry for such a long post.

 Tudor Miron March 9, 2004 08:11

Hi All, I allready figured that model came in "scaled" - became a very little tiny thing ;). It was created in SolidWorks using inches. I imported it again and this time left database units as default. In Build when in geometry I choused inches and when created a point with inch aoordinates it apeared where it had to. I'll rerun the model now and will report the results. Still have main questions: What IS the correct conditions to model flow around car body. Any hints and suggestions will be highly appritiated. One persone from Ford Racing (he was not doing CFD but was supervising all project) told me that it took me two! years to come up with model that corelated with wind tunnel testing.... That makes me worryed... Does it mean that CFD is useless (race car aero)if I don't have wind tunnel handy to corelate results? I really hope that this is not the case... Thank you Ted

 Tudor Miron March 9, 2004 10:43

I reruned the model with coarse mesh (221000 nodes)and when in SFXC-Post got more realistic numbers. L = 1262[N], D = 115.108[N]. This was not a model of real car but a blunt body with inclouded tunnel. Small frontal area 0.12m^ (1.34ft^) and kind of inverted airfoil shape running close to the ground suggest that this numbers might be slose. When tryed to calculate Cd I thought that I should take "plane" area as is used when calculating Cd of airfoils. So Cd = D/(0.5 x 1.22 x 44.44^ x 1.94) = 0.047 I don't know if it sounds realistic for such a model. If I calculate it using frontal area than I get Cd = D/(0.5 x 1.22 x 44.44^ x 0.12) = 0.79. Ld using same formula = -0.54 How ever when I calculated area of model it showed 4.8M^ and SolidWorks where model was made shows 5.01M^ ... Difference is not THAT big but still it's confusing Any suggestions will be highly apreciated.

Thank you Ted

 Glenn Horrocks March 9, 2004 18:57

Hi Ted,

It does not surprise me it took a guy from Ford Racing two years to get good agreement. A good model of something as complex as car external aerodynamics is a very difficult assignment. That does not mean CFD is useless without wind tunnel data, it just means you need to do some homework. Wind tunnel data is very useful if you can do it, but if you can't you should look at the literature.

The main foundation paper in this field was done by Ahmed (hence the Ahmed body). It forms the basis of one of the tutorial problems in CFX 5.6. I think there is a reference to this paper in the documentation. Get a copy of this paper, and try to reproduce his results. Many authors since then have used this shape to benchmark the accuracy of their simulations since then, so you should also be able to uncover many more recent papers using the same model.

Also look for literature on car aerodynamics in general. There's lots of published works on this topic out there.

Glenn

 Tudor Miron March 10, 2004 08:05

Hi Glenn, Thanks a lot for your help. While I found some resent SAE papers referring to Ahmed body: 2004-01-1308, 2004-01-0442, 2002-01-3349, 2001-01-2742, 942498 I could not find Ahmed's paper itself. Could you please give its number or full name? Also are there any other papers that you would recommend? Also I have some more dumb questions: 1) Is Physical timescale 1/3 of time that fluid takes to flow through domain good enough? Could I use automatic timescale? 3) Currently I'm setting simulation as steady-state, is it proper way? 4) What is proper convergence target? 1e-4? 1e-6? I've heard from one person that decent results can be had with 1e-3… that would be nice ;) 5) What turbulence (SST) options should I use? Currently I was using Medium 5%. 6) As indicated in earlier posts I had problems (dimension wise) when importing iges file to Build. Even now when model is close to it's CAD size, calculating "area" in CFX-Post I get slightly different numbers than in SolidWorks for same model – any suggestions.

Thank you very much for you help! Your input is invaluable and highly appreciated.

Thank you Ted

 Glenn Horrocks March 10, 2004 18:01

Hi Ted,

On the CFX community page there is an extended Ahmed body example where they give the full reference:

http://www-waterloo.ansys.com/cfxcom...Ahmed_Body.htm

To answer your questions: 1) In a steady state flow, adjust the timestep to give best convergence speed. Don't be too worried about it, if you don't have the optimum number you will just have to do a few more iterations to get to convergence.

2) Question seems to have disappeared!

3) If you are looking for the time averaged response, then yes. As long as it converges acceptibly this will do. If you are interested in the vortex shedding off the back or are having convergence problems then no.

4) Convergence levels are discussed in the following document: http://www-waterloo.ansys.com/cfxcom...onvergence.htm

5)I assume you are talking about initial and inlet turbulence conditions. The initial turbulence condition does not matter as it gets blown away during the simulation (as long as it is not too wildly off then it won't converge). The inlet turbulence levels are dependant on what you are trying to model - for instance a windy day or other vehicles in the vicinity. Also, often the inlet turbulence levels do not make a huge difference to the answer (but sometimes they do!).

6) CFX-Post will give slightly different values for volumes and areas as it is calculating it based on the discretised shapes, that is the shape of the elements. SolidWorks hopefully uses the exact geometry.

Regards, Glenn

 Neale March 10, 2004 22:07

1. 1/3 is pretty good. If you experience robustness problems then 1/4-1/5 may be necessary. The rule is use the biggest timestep you can get away with.

3. Probably steady state is just fine for lift/drag, unless you are interested in simulating transient vortex shedding off the geometry or something.

4. Read the convergence doc already pointed out by Glenn. 1.0e-3 MAX is good for ballpark solutions and 1.0E-4 should be used if you want "final" results.

5. SST is a pretty good choice. To get best results though you need a really good boundary layer grid with at least 5-10 prism layers in the boundary layer. Inlet turbulence levels usually don't have to be touched. However, in some cases, if you are running a domain where the inlet is *far* upstream of the car then the turbulence can die out by the time it reaches the car and the flow is essentially running laminar around the car. This usually results in non-convergence or robustness problems which it sounds like you are not having.

In addition, you might for interest also read through the CFX Validation report or DES:

http://www-waterloo.ansys.com/cfxcom...on/default.asp

It discusses Ahmed body results. The focus is DES but they also used SST and other models as well.

Neale

 Tudor Miron March 11, 2004 16:44

Glen, Neale, You guys ROCK! Your help is highly appreciated. As far as I understood with inlet turbulence model I can simulate my car running in "clean" or disturbed air. How ever if inlet is far from model than it will "dissolve" before reaching model and it would not solve – hope that I got it right. In CFX tutorial 5, using Ahmed body, Author suggests to use for inlet b/conditions intensity and length scale option for turbulence with 0.05 value for fractional intensity and 0.1m for Eddy length scale. Should I consider this as "clean" air stream? As mentioned in previous posts I used 5%. Here another question arises – if I want to simulate my car fallowing a competitor closely (inlet as close as virtual competitor simulated)– what turbulence option I should use? This condition is known to cause drop in both drag and lift allowing faster straight line speed but possible problems in fast sweeping corners. One very dumb question – how many prism layers I have in boundary layer when setting inflation parameter?

I did comparative runs with different convergence target. Here's results:

1e-3 1e-4 1e-5 L = -1013.17N L = -1222.83N L= -1304.7 D = 87N D = 108.6N D = -114

I guess this is because of the nature of my model. How can I upload a file (text or image) to this forum? My model is not a car yet but a blunt body with horizontal upper surface and inverted airfoil shape lower surface. Side "skirts" 1.5" from ground and 1.38" from "tunnel" lowest part. 106" long and 58" wide. Looking at model in CFX-Post big part (may be main part) of downforce is caused by air leaking from sides into lower pressure area after tunnel upsweep. This air creating vortex – very fast as they get under car. This causes low pressure zones. It also helps the flow to stay attached to tunnel surface – in the longitudinal middle of tunnel where vortexes don't influence flow seem to separate about 18" from end of tunnel. Closer to sides where vortexes exist flow stays attached. I suspect that because of this vortexes finer convergence gives different numbers. If this is the case I guess that I just have to keep raising the bar till results stabilize. May be I'm wrong and this difference in results indicates some problem in the way I set the simulation. As model is symmetric I run a half only but it's seems to be wrong as those vortexes are pointing towards car centerline. So If I run it as full model they should interact probably canceling each other. I'd like to kindly ask you to take a look at part of my output file. May be there's some obvious mistakes? I know that this information is by far not enough but I can upload needed files to FTP if necessary.

I'll have to ask about license number to be able to log into CFX community forum. As I told you I don't own the program but friend of my kindly giving me some "machine time" – I don't know what his boss will say about giving me license number to log in…

Once again I want to say THANK YOU for your help. Ted

SIMULATION TYPE :

END

DOMAIN : JT2

Coord Frame = Coord 0

Domain Type = Fluid

Fluids List = Air Ideal Gas

Location = JT1

DOMAIN MODELS :

BUOYANCY MODEL :

Option = Non Buoyant

END

DOMAIN MOTION :

Option = Stationary

END

REFERENCE PRESSURE :

Reference Pressure = 1e05 [Pa]

END

END

FLUID MODELS :

COMBUSTION MODEL :

Option = None

END

HEAT TRANSFER MODEL :

Fluid Temperature = 288 [K]

Option = Isothermal

END

Option = None

END

TURBULENCE MODEL :

Option = SST

END

TURBULENT WALL FUNCTIONS :

Option = Automatic

END

END

BOUNDARY : Inlet

Boundary Type = INLET

Location = Inlet

BOUNDARY CONDITIONS :

FLOW REGIME :

Option = Subsonic

END

MASS AND MOMENTUM :

Normal Speed = 44.44 [m s^-1]

Option = Normal Speed

END

TURBULENCE :

Option = Medium Intensity and Eddy Viscosity Ratio

END

END

END

BOUNDARY : Outlet

Boundary Type = OUTLET

Location = Outlet

BOUNDARY CONDITIONS :

FLOW REGIME :

Option = Subsonic

END

MASS AND MOMENTUM :

Option = Average Static Pressure

Relative Pressure = 0 [Pa]

END

END

END

BOUNDARY : FreeWalls

Boundary Type = WALL

Location = FreeWalls

BOUNDARY CONDITIONS :

WALL INFLUENCE ON FLOW :

Option = Free Slip

END

END

END

BOUNDARY : SimP

Boundary Type = SYMMETRY

Location = SimP

END

BOUNDARY : BodyJT2

Boundary Type = WALL

Location = BodyJT1

BOUNDARY CONDITIONS :

WALL INFLUENCE ON FLOW :

Option = No Slip

END

END

END

END

INITIALISATION :

Option = Automatic

INITIAL CONDITIONS :

Velocity Type = Cartesian

CARTESIAN VELOCITY COMPONENTS :

Option = Automatic with Value

U = 44.44 [m s^-1]

V = 0 [m s^-1]

W = 0 [m s^-1]

END

EPSILON :

Option = Automatic

END

K :

Option = Automatic

END

STATIC PRESSURE :

Option = Automatic

END

END

END

SOLVER CONTROL :

Option = High Resolution

END

BODY FORCES :

Body Force Averaging Type = Volume-Weighted

END

CONVERGENCE CONTROL :

Maximum Number of Iterations = 100

Physical Timescale = 0.125 [s]

Timescale Control = Physical Timescale

END

CONVERGENCE CRITERIA :

Residual Target = 1e-5

Residual Type = RMS

END

DYNAMIC MODEL CONTROL :

Global Dynamic Model Control = Yes

Data Type Kwords Words/Node Words/Elem Kbytes Bytes/Node

Real 121256.0 331.07 90.85 473656.1 1324.29 Integer 48686.4 132.93 36.48 190181.2 531.73 Character 1450.5 3.96 1.09 1416.5 3.96 Logical 40.0 0.11 0.03 156.2 0.44 Double 908.0 2.48 0.68 7093.8 19.83

+--------------------------------------------------------------------+ | Total Number of Nodes, Elements, and Faces | +--------------------------------------------------------------------+

Domain Name : JT2

Total Number of Nodes = 366251

Total Number of Elements = 1334664

Total Number of Tetrahedrons = 979224

Total Number of Prisms = 355440

Total Number of Faces = 84272

Execution terminating: all RMS residual AND global imbalance are below their target criteria.

================================================== ====================

Boundary Flow and Total Source Term Summary ================================================== ====================

+--------------------------------------------------------------------+ | U-Mom | +--------------------------------------------------------------------+ Boundary : BodyJT2 6.2704E+01 Boundary : FreeWalls -8.3726E-01 Boundary : Inlet -3.1629E-05 Boundary : Outlet -2.6912E+02 Boundary : SimP 2.0535E+02

----------- Domain Imbalance : -1.9046E+00

Domain Imbalance, in %: -0.0202 %

+--------------------------------------------------------------------+ | V-Mom | +--------------------------------------------------------------------+ Boundary : BodyJT2 1.3047E+03 Boundary : FreeWalls -1.2674E+03 Boundary : Inlet -5.1498E-06 Boundary : Outlet -3.7485E+01

----------- Domain Imbalance : -1.7258E-01

Domain Imbalance, in %: -0.0018 %

+--------------------------------------------------------------------+ | W-Mom | +--------------------------------------------------------------------+ Boundary : BodyJT2 1.1404E+02 Boundary : FreeWalls -3.2405E-04 Boundary : Inlet -9.4220E+03 Boundary : Outlet 9.3072E+03

----------- Domain Imbalance : -7.5684E-01

Domain Imbalance, in %: -0.0080 %

+--------------------------------------------------------------------+ | P-Mass | +--------------------------------------------------------------------+ Boundary : Inlet 2.0814E+02 Boundary : Outlet -2.0814E+02

----------- Domain Imbalance : -2.0294E-03

Domain Imbalance, in %: -0.0010 %

================================================== ====================

Wall Force and Moment Summary ================================================== ====================

Note: Pressure integrals exclude the reference pressure. To include

it, set the expert parameter 'include pref in forces = t'.

+--------------------------------------------------------------------+ | Pressure Force On Walls | +--------------------------------------------------------------------+

X-Comp. Y-Comp. Z-Comp. BodyJT2 -6.3521E+01 -1.3049E+03 -9.5062E+01 FreeWalls 8.3525E-01 1.2635E+03 0.0000E+00

+--------------------------------------------------------------------+ | Viscous Force On Walls | +--------------------------------------------------------------------+

X-Comp. Y-Comp. Z-Comp. BodyJT2 8.1729E-01 1.9257E-01 -1.8977E+01 FreeWalls 1.9481E-03 3.9170E+00 3.2405E-04

+--------------------------------------------------------------------+ | Pressure Moment On Walls | +--------------------------------------------------------------------+

X-Comp. Y-Comp. Z-Comp. BodyJT2 -7.6300E+02 1.7431E+02 -5.4323E+02 FreeWalls 6.2944E+02 1.0596E+03 5.0946E+02

+--------------------------------------------------------------------+ | Viscous Moment On Walls | +--------------------------------------------------------------------+

X-Comp. Y-Comp. Z-Comp. BodyJT2 -2.1958E+00 7.2550E+00 -1.5856E-01 FreeWalls 7.8970E+00 -8.1475E-03 -5.5444E-01

+--------------------------------------------------------------------+ | Locations of Maximum Residuals | +--------------------------------------------------------------------+ | Equation | Node # | X | Y | Z | +--------------------------------------------------------------------+ | U-Mom | 12249 | 7.281E-01 | 0.000E+00 |-5.989E-01 | | V-Mom | 12249 | 7.281E-01 | 0.000E+00 |-5.989E-01 | | W-Mom | 36418 | 0.000E+00 | 5.576E-02 |-5.842E+00 | | P-Mass | 74048 | 0.000E+00 | 1.184E+00 |-5.842E+00 | | K-TurbKE | 125541 | 7.188E-01 |-2.557E-03 |-6.173E-01 | | O-TurbFreq | 12021 | 7.197E-01 | 0.000E+00 |-6.168E-01 | +--------------------------------------------------------------------+

+--------------------------------------------------------------------+ | Peak Values of Residuals | +--------------------------------------------------------------------+ | Equation | Loop # | Peak Residual | Final Residual | +--------------------------------------------------------------------+ | U-Mom | 1 | 5.29802E-05 | 6.75326E-06 | | V-Mom | 1 | 2.63665E-05 | 2.38653E-06 | | W-Mom | 1 | 9.03116E-05 | 9.93734E-06 | | P-Mass | 1 | 1.31405E-05 | 1.38309E-06 | | K-TurbKE | 1 | 1.64213E-04 | 9.63895E-06 | | O-TurbFreq | 2 | 1.92829E-04 | 1.50320E-05 | +--------------------------------------------------------------------+

+--------------------------------------------------------------------+ | False Transient Information | +--------------------------------------------------------------------+ | Equation | Type | Elapsed Pseudo-Time | +--------------------------------------------------------------------+ | U-Mom | Physical | 5.99540E+00 | | V-Mom | Physical | 5.99540E+00 | | W-Mom | Physical | 5.99540E+00 | | P-Mass | Physical | 5.99540E+00 | | K-TurbKE | Physical | 5.99540E+00 | | O-TurbFreq | Physical | 5.99540E+00 | +--------------------------------------------------------------------+

+--------------------------------------------------------------------+ | Average Scale Information | +--------------------------------------------------------------------+

Domain Name : JT2

Global Length = 3.3930E+00

Maximum Extent = 1.0160E+01

Density = 1.2050E+00

Dynamic Viscosity = 1.7900E-05

Velocity = 4.6116E+01

Reynolds Number = 1.0534E+07

Speed of Sound = 3.4057E+02

Mach Number = 1.3541E-01

 Glenn Horrocks March 11, 2004 17:13

Hi Ted,

With respect to your different residuals and the lift and drag they predict: As the lift, and especially the drag is still moving around with different convergence levels, this indicates that you have not yet reached a properly converged solution.

1) Your tightest convergence is 1e-5 (RMS) which is pretty tight, but the problem with RMS residuals is there can be a small region of high residuals which get offset by the far greater region of lower residuals resulting in premature convergence. I bet the local high residuals are in the wake region behind the car, and this region would have a large effect on the L & D figures. I would recommend repeating with MAX residuals.

2) You may not be reaching a fully converged solution because of a grid problem. Almost always this means your grid is too coarse, especially in the "difficult" region, which is the rear of any bluff body where the seperations occur. If you can, try a finer grid.

Regards, Glenn

 Tudor Miron March 11, 2004 17:36

Thank you Glen, I don't have much more CFX time tonight so could you please point me: should I first refine the mesh or should repeat with MAX residuals first. Also to my shame I don't know how to repit with max residual :(

Thank you Ted

 Bob March 14, 2004 08:21

Hi Ted, to set the maximum residuals you set them in the solver control section, you should be able to see the GUI set to RMS residuals and a value. If time is an issue then always better to go for the faster option, ie in your case change the residuals, as chjanging the mesh will take some time and you may not have anything to run when your time is up !

Another suggestion is to monitor the forces on your basic car shape. If you have a wall boundary condition defined that covers all of your car surfaces and nothing else, you can then monitor the forces on this boundary condition. To do this goto the solver manager and create a new monitor trace (not sure what they call this officially as I'm not infront of a CFX machine), then right click on the window, and choose the monitor properties, and pich the forces option. There you will be able to pick the stream wise force and also the vertical force for that boundary. These traces will give you a feel for how well the drag and lift are converging.

Hope this helps and sorry for not being able to remember the exact names of some of the GUI's

Bob

 Tudor Miron March 15, 2004 17:23

Thank you Bob, How ever for a day or two I woudn't be able to work with CFX. My sun is ill :( so I can't stay late at work. But I'll try your suggestions as soon as I get to CFX machine. In the meantime I'd like to ask if someone will take a look at "physics conditions" I'm aplying in PRE for this problem - does it look right? Also as Neal stated to get advantage of SST model I should have at list 5 layers within boundary layer. Question is HOW DO I KNOW how many layers I have? Again sorry for dumb question.

Thank you Ted

 Neale March 17, 2004 01:37

Tudor,

Your physics setup looks fine. I would just turn off the body force averaging though, that does not matter for your case.

You will know how many inflation layers you have because you should have set this when you created the mesh in CFX-Build. You can control these settings in Build using Set->Inflation Parameters on the meshing panel.

You could also load the grid into CFX-Post, throw a slice plane across your body and just count how many prisms you see before the mesh turns into tetrahedrons.

If you don't have at least 5-10 prism layers in the boundary layer you will not get good drag predictions. Lift may be OK, but drag will not be.

As for inlet BCs, my comment about turbulence dying out only applies if your inlet BC is far upstream of the car. say 50 car lengths or something like that. This does not sound like it is your case.

Probably 5% and default length scale are just fine for your turbulence conditions. Even if you are trying to simulate a car just in front I would not go higher than 10% or so.

If you have converged to 1.0 E-5 RMS residuals you should simply check how far the MAX residuals have come in. In some cases, if the flow is not hung up on some bad grid (as described by Glenn) the MAX residual will follow RMS by an order of magnitude (1.0E-4 in your case). Just right click in the solver manager and select "switch residual mode" to check where the MAX values are at. If these are 1.0E-3 or below you can probably be pretty sure you have a reasonable solution on your current grid. You could try, if you want, to get it to 1.0E-4 MAX but this may only be possible if you have enough grid resolving all "tough" regions of your flow.

Since your flow is basically incompressible, one other thing you might try is running a constant blend factor advection model instead of high-resolution. Just switch this on the solver control panel and set a value of 1.0. This will run a bit faster and you may get a better result than with high-res. Caveat is that you may encounter some robustness/convergence difficulty (eg: not being able to get MAX residuals down or something like that), which may require grid refinement.

Make sure you plot the force on the car in the solver monitor as well, to see if it is changing. If it is not, or is oscillating around some average value, then you can assume that the solution is complete.

Neale

 Tudor Miron March 17, 2004 16:15

Thank you Neale, First I have to say that I do know how many prism layers I have as I set them myself…. But how do I know how many I have within a boundary layer? Or I'm overenthusiastic here? I thought that CFX manual wanted me to have at list 5 – 10 layers WITHIN boundary layer… they never told should it happen at front or rear section of car …. Now to convergence problems that I had. I really think that this was those 2600 flat tetrahedral elements that outfile "noticed". Refining mesh control to 7.5mm didn't help. What did help is reducing number of inflation layers from 20 to 5. This left me with only 3 flat tetra elements and solution converged to 1E-04 nicely. How ever I think that this was a problem in fairly small bit of mesh as force results was very close in previous run (one fluctuating at 1E-4.8 for about 50 iterations and last one) but this is bothering me…. I would really like to find solution for this kind of problems (fixing the mesh) without reducing number of layers. One guy told me that in this case I should run a transient solution – he says that otherwise fluctuations can not be solved without coarsening the grid…. Never tried a transient yet. It was stated in this thread that I don't need transient unless I want to study vortex shedding off the rear of car model. I actually very interested in accurate vortex prediction as it plays major role in my underbody aerodynamics – I'm trying to do something similar as older group C cars. Any suggestions? Also I'd like to ask is there some rule of thumb for fluid domain size when working on automotive solutions? Thank you Ted

 Glenn Horrocks March 17, 2004 17:36

Hi Neale, ted,

You will have to get rid of these flat elements before it will converge nicely. Forget about transient issues, RMS/MAX convergence and everything else until you have a grid with no flat elements.

Have a look at my other posting on this issue, hopefully it can help you get rid of the flat elements.

Glenn

 Tudor Miron March 17, 2004 18:10

Even if I have only 4 flat elements in 1700000 elements grid?!?! Is it that important? Any way I'm off to read your post on this issue. Thank you Ted

 Glenn Horrocks March 18, 2004 17:44

Hi Ted,

Yes, it is important. Sometimes you can still get it to converge, but sometimes not. Either way, convergence will be much faster and more reliable without them. The MAX residuals are the maximum residual in the simulation, and that is likely to occur at the flat element so it is likely to be the area slowing convergence.

Glenn

 Neale March 19, 2004 20:23

Sorry Tudor, I misintrepreted your question before.

You can get a rough idea in CFX-Post of how well resolved your boundary layer is. In some slice planes take a look at how the velocity vectors vary from the car body to the free stream. Is there a nice profile or do you have like 2 vectors in most spots. That's all. You can look at yplus values as well but this is not so important if you are running SST.

As Glenn also points out, if you have a nice grid you wont need transient uless you want to see the vortex shedding and how the drag varies in the transient due to that. Steady state is fine for getting the "averaged" value.

If you are getting flat elements they you need to narrow in on the region where these are occuring and try putting in a bunch of mesh controls. You could also, as you point out, play with the number of inflation layers. 20 sounds like a lot. The bad elements can be the reason the residuals are hanging up so you should look at the end of the solver output file and find the node numbers of where the max residuals are located. Make a point locator in CFX-Post and see if that position corresponds to your bad grid at all, it probably will.

Neale

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