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SAE TECHNICALPAPER SERIES 983041
Viscous-Flow Simulation of an Open-WheelRace Car
Joseph KatzSDSU
Hong Luo, Eric Mestreau and Joseph BaumSAIC
Reinald LhnerGeorge Mason Univ.
Reprinted From: 1998 Motorsports Engineering Conference
ProceedingsVolume 1: Vehicle Design and Safety
(P-340/1)
Motorsports EngineeringConference and Exposition
Dearborn, MichiganNovember 16-19, 1998
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1983041
Viscous-Flow Simulation of an Open-Wheel Race Car
Joseph KatzSDSU
Hong Luo, Eric Mestreau and Joseph BaumSAIC
Reinald LhnerGeorge Mason Univ.
Copyright 1998 Society of Automotive Engineers, Inc.
ABSTRACT
A numerical solution based on the Navier-Stokes equa-tion,
combined with unstructured grid mesh, was used tomodel an open
wheel race car. The solution is based ona fast, matrix-free,
implicit method, with relatively lowstorage requirements, resulting
in solution times up to anorder of magnitude smaller than other
numerical solu-tions. The computations provide details on the flow
fieldaround the car and a complete pressure distribution onthe
vehicles surface. The calculated results may be usedas a
supplementary tool for wind tunnel or road testingand can provide
information, such as the underbody flow,which is difficult to
evaluate experimentally. One of theprimary advantages of such a
viscous flow simulation isthe ability to model wheel rotation and
to detect regionsof flow separation, particularly on the suction
side of thefront and rear wings.
INTRODUCTION
The complex nature of the flowfield over open-wheel racecar
configuration often results in numerous non-lineareffects which
complicate the estimation of expected per-formance-gains due to
proposed design modifications.Traditionally, both wind-tunnel and
road tests are usedextensively during the aerodynamic development
of sucha vehicle. Those methods have matured to providedependable
integral results such as the lift and drag butquite often cannot
provide sufficient details on the flow-field to explain why certain
trends are observed. There-fore, a design tool that can provide
detailed flow-information on and off the surface of the vehicle,
can helpexplain some of those nonlinear effects and shorten
thedesign cycle. To fill this void, recently, the use of
comple-mentary computational methods has increased [1-3] andtheir
significance as an additional independent designtool has been
gradually established. Earlier computa-tional tools were limited by
computer performance and
initially inviscid methods were used, with some success[4], for
various race cars and road vehicles with largeregions of attached
flows. Because of the massive flowseparations, particularly those
created by the largewheels, viscous flow simulation is necessary
for openwheel race cars. Consequently, the solution of the
fullNavier-Stokes (N.S.) equations is required for the flow-field
surrounding the complex geometry of an INDY-typerace car, such as
the one shown in Fig. 1.
Figure 1. Solid body model of a generic INDY race car.
The objective of the present work is to demonstrate
theapplicability of the approach as a complementary
tool,particularly in areas where the experimental approachhas
limited capabilities. For example, flow-visualizationinside the
diffusers under the car, as well as tracing thefront wing wake in a
high-Reynolds number flow, is closeto impossible in a wind tunnel
experiment. Similarly, eval-uating the pressure distribution over a
large number ofproposed wing configurations, in a small-scale test,
maybecome an endless chore. In all these cases, the use of
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2computational methods can easily fill the required infor-mation
gap.
METHODOLOGY
The present work is based on solving the finite
elementequivalent of the N.S. equations with the
flux-correctedtransport concept (Ref. 5). An unstructured mesh is
usedwhich makes the grid generation around complex config-uration
much simpler than with other structured gridmeshes. The process
usually begins with the preproces-sor FECAD that prepares the CAD
surface for the gridgenerator, FRGEN3D. The grid generator then
createsthe computational mesh, which is used by the
solver,FEFLOW97/8, that solves the finite-element equivalent ofthe
N.S. equations. A post processor (FEPOST3D) isthen used to
graphically display and analyze the compu-tational results. These
utilities are briefly described in thefollowing
paragraphs.Generation of the vehicle surface model is still one of
thelargest tasks in the process of obtaining a numerical solu-tion.
The experience gained over several years in thegeneration of
surface and volume meshes for the simula-tion of flows about such
complex geometric structures asairplanes, tanks, trains, cars and
trucks [6-8], has shownthat once the surface and volume mesh
generation hasbeen automated, the surface description (i.e., point,
lineand patch definition), as well as the correct definition
ofboundary conditions, become the dominant time con-suming task.
This information led to the development ofthe preprocessor FECAD, a
suite of efficient, user-friendly utilities that allows the quick
production ofFRGEN3D-compatible, error-free input. In addition
tobasic CAD-CAM operations (shrinking, translating, rotat-ing,
surface lofting, etc.), FECAD also eases the mergingof several
surface parts into one cohesive, well-definedinput-file. This
allows the merging of files produced by dif-ferent users and/or
different surface generators. Mostimportantly, FECAD allows
graphical interrogation of thesurface data, and has many built-in
diagnostics to avoidundesirable features such as doubly defined
points, iso-lated points or lines, badly defined lines or surfaces,
andlines or surfaces that are directed incorrectly. FECADalso
allows the specification and visualization of bound-ary conditions,
saving the user many error-prone hoursduring the later stages of a
run. FECAD has proven to bean invaluable aid when trying to
construct an error-freeFRGEN3D-compatible input file in a matter of
days oreven hours. In order to specify the desired element sizeand
shape distribution in space, a combination of back-ground grids [9]
and sources is employed. This task isagain performed within the
point-and-click environment ofFECAD.The solid body model of a
generic INDY car, created bythe FECAD preprocessor is shown in Fig.
1. The modelincludes simulation of the internal flow across the
radiatorducts and the proper boundary conditions to simulatewheel
rotation and moving ground. More details on thegeometry and
specific dimensions of this vehicle can be
found in the 1996 rulebook [10] of the sanctioning organi-zation
(CART).The grid generator used is FRGEN3D [9]. This unstruc-tured
grid generator is based on the advancing frontmethod. After
defining the surface of the domain to begridded, the surfaces are
triangulated. Thereafter, theface that forms the smallest new
element is deleted fromthe front, and a new element is added. This
process isrepeated recursively until no more faces are left in
thefront. Results of the grid generation are presented in Fig.2.
and the triangular surface elements density can beeasily adjusted
in areas where larger resolution isrequired, without dramatically
increasing the total numberof grid points. The mesh used in this
computationassumes a symmetrical model and contains
8,314,454tetrahedral elements, 1,459,199 grid points, and
uses174,134 boundary points on the car surface and the farfield
(per one half of the model).
Figure 2. Unstructured grid around the open-wheel race car
model. To simulate a moving ground, the wheels rotate in
coordination with the speed of the floor grid.
The flow solver employed was FEFLO97, a new 3-D ALEedge-based
[11] hydro-solver based on the Finite-Ele-ment Method
Flux-Corrected Transport (FEM-FCT) con-cept [5], which solves the
Euler and Reynolds-averagedturbulent, Navier-Stokes equations.
H-refinement is thepreferred approach for grid adaptation [12]. The
high-order scheme used is the consistent-mass Taylor-Galer-kin
algorithm. Combined with a modified second-orderLapidus artificial
viscosity scheme, the resulting schemeis second-order accurate in
space, and fourth-orderaccurate in phase. The spatio-temporal
adaptation isbased on local H-refinement, where the
refinement/dele-tion criterion is a modified H2-seminorm [12]. The
criticalparameter for the refinement/deletion criteria is
density.Various turbulent models can be used, and the model was
tested successfully with this approach. Forthe calculations
presented here a full-size vehicle at 100mph was simulated;
however, no turbulence model was
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3used and the data represents a virtual high-Reynoldsnumber
laminar flow case. When compared with experi-mental data, this
temporary simplification typically resultsin earlier flow
separation on highly curved surfaces.The FEFLO98 solver has
recently been improved with anew, fast, matrix-free implicit
algorithm. This algorithmsolves an approximate system of linear
equations whicharise from the Newton linearization by the GMRES
(Gen-eralized Minimum RESidual) algorithm with a LU-SGS(Lower-Upper
Symmetric Gauss-Seidel) preconditioner.This preconditioner has been
further modified to allowthe accurate solution of virtually
incompressible flows(i.e., down to Mach numbers of 0.00001). The
mostremarkable feature of the new GMRES+LU-SGS methodis that the
storage of the Jacobian matrix can be com-pletely eliminated by
approximating the Jacobian withnumerical fluxes, resulting in a
matrix-free implicitmethod. Numerical tests demonstrate a factor of
10-15increase in performance over the best current implicitmethods,
without increasing memory requirements. Inthis particular case, the
residual is reduced by threeorders of magnitude within 200 time
steps and the wholecomputation requires about 5 hours of CPU time
(on aCray C-70 computer).Post-processing was performed with the
FEPOST3D andFEMOVIE packages [13]. FEPOST3D performs all
CPU-intensive filtering operations on the Supercomputer. Onlythe
plane or surface data are sent back to the graphicsworkstation for
plotting.
Figure 3. Streamline traces in the flow under the car.
RESULTS
Results of the computations are divided into two sections.The
first is the off-body flow visualization and the sec-ond is the
surface pressure distribution. Flow visualiza-tions are widely used
during wind-tunnels experiments;however, in some areas conventional
methods are notalways effective. Similarly, surface pressure
measure-ments may be measured in a wind tunnel but are notwidely
used in race-car wind tunnels because of the shortdevelopment time
requirement.
Typical streamline traces in the flowfield nearby the carmodel
are presented in the following six figures. Thesefigures, as viewed
in the post-processor, are far moredetailed and use colors to
identify the local velocity on thestreamline. Unfortunately, most
of the resolution and theaerodynamic information is lost while
converting thoseflow visualizations into the gray-scale images in
this arti-cle. An example of such streamline traces is shown inFig.
3. The tracing begins behind the front wheels andthe fluid
particles are partially captured by the large sepa-ration zone
behind the wheel. Some slow moving parti-cles may rise in the flow
behind the wheel and join thehigh speed stream above it. To
simulate actual road con-dition the tire had a flat contact patch
with the road whichwas further modified by two small wedges
insertedunderneath. This was done to improve local
numericalstability and was plotted by the postprocessor as an
ele-vated block (see Figs 3 and 4). Also, the effect of thesmall
turning vane in front of the side pod is clearly visibleI this
figure. The flow is kept attached to the bodyworkand is less
affected by the wheel-base separation. Thestreamlines above the
wheel seem to head inward andeventually will end up flowing beneath
the rear wing.
Figure 4. Streamline traces released in the vehicle symmetry
plane.
The streamline traces shown in Fig. 4 provide a
generalindication about the flow direction in the symmetry
plane.The raised nose design clearly allows sufficient flowunder
the vehicle, but most of the flow moving above thenose will end up
near the drivers helmet. The rear wingclearly changes the
streamline curvature, indicating thelarge level of downforce
created. However, the stream-lines leaving the trailing edge flap
are not parallel to theflap due to local flow separation there.
This separationmay be exaggerated by the current computation
butsome partial flow separation was observed during roadtesting
with the higher downforce settings. The lack ofstreamlines behind
the lower portion of the vehicle mayindicate the high bluff body
drag created.The information about the orientation of the flow
ahead ofthe vehicle is relevant to both downforce and cooling
con-siderations. Fig. 5 and Fig. 6 demonstrate how some ofthis
information can be obtained by using numerical flow
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4visualizations. For example, the raised central portion ofthe
front wing allows more flow to move under the car,which eventually
contributes to more airspeed there andmore downforce. But, more
importantly, this portion of theflow seems to reach the cooling
inlets, directly affectingthe side pod design. The streamlines in
Fig. 6 show thatsome of the flow at the wing root still reaches the
coolingducts, but most of the streamlines travel above the vehi-cle
side pod. Once the airflow moves past the side pods(Figs. 5 and 6),
it is channeled below the rear wing. Acareful examination of the
streamlines near the front wingtip, in both figures, indicates that
the tip-vortex stretchesinside the front wheels and then moves
outside andupward, missing the rear wing.
Figure 5. Streamline traces released at the front wing leading
edge level.
Figure 6. Streamline traces released above the front wing
leading edge plane.
The high suction of the rear wing is evident in Fig. 7 aswell.
Here the streamlines were released in a plane out-side the front
wheels. The flow initially is displaced out-ward by the large
rotating wheels; however, the suctionbehind the front wheels turns
some of the streamlinesinward. A large portion of the streamlines
eventually rises
above the rear bodywork and travels under the large rearwing.
The effect of the small flow turning device abovethe rear wing may
be clarified by observing the stream-lines in this area. Because of
the locally horizontal flow ithas the potential to create some
downforce, and at thesame time reduce the rear wheel drag by
diverting theflow away from it.
Figure 7. Streamline traces released outside of the front wing
side fin.
The top view of the flow approaching the rear wing isshown in
Fig. 8. The boat-tail shape of the body and thelarge suction under
the rear wing is forcing the flow tomove inward between the rear
wheels and the body. This,in effect, creates an angularity in the
direction of the flowreaching the rear wheel and the rear
separation bubblefaces inward. Further behind the car, after
passing therear wing, the streamlines are closing inward quickly.
Thisis most likely a reaction to the low pressure base flow
(orbluff body effect) of the not so streamlined vehicle andits
wheels and due to the flow induced by the rear wingvortices.
In the second part of this article, calculated surface pres-sure
data is presented. The surface pressure distributionis a direct
outcome of the copmputations and readilyavailable on all surfaces.
By integration, it can be used todetermine aerodynamic loads on
various body panelsand can be used to redesign a particular surface
shape(e.g. to reduce flow separation). As an example, the pres-sure
distribution along the ground-plane symmetry line ispresented in
Fig. 9. The front suction peak is created bythe front wing, while
the second one is a result of the flowaccelerating between the
front wheels. The largest suc-tion peak is at the entrance to the
underbody tunnels(which still exist in INDY cars), and the pressure
coeffi-cient then gradually increases to values near zero behindthe
vehicle. The experimental data shown by the (*) sym-bols was
collected by a static pressure rake behind thecar, and it agrees
reasonably well with the computed val-ues.
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5Figure 8. Top view of the streamline traces approaching the
rear wing.
Figure 9. Pressure distribution on the moving ground plane
centerline.
Experimental evaluation of the pressure distribution onmoving
surfaces, such as shown in Fig. 9, is quite diffi-cult,
particularly when it comes to rotating wheels. Fig. 10demonstrates
such results when using the computationswith a rotating surface.
Here the pressure distributionalong the wheel centerline is
presented in a polar dia-gram (note that the Cartesian ordinates
serve to indicatethe Cp magnitude only, but the pressure
distributionshown is wrapped around the circular tire outline). In
frontof the tire, at the lower part of the wheel, a high
pressurearea exists (positive is inside the circle, on which Cp
=0),and the loop in the data shows the pressures on theground as
well. As the flow accelerates over the wheel,the pressure
coefficient drops and reaches negative val-
ues above the wheel. The small dip near the top of thetire is
probably due to the flow separation line there. Thissuction region
inside the separated region, extends witha fairly constant pressure
coefficient behind the wheel,clearly contributing to the drag force
on this wheel.The pressure distribution (or velocity distribution)
on awing can serve to evaluate its performance and indicate ifits
lift or drag can be altered according to a particulardesign need.
For example, the pressure distributionalong longitudinal sections
of the race cars front and rearwings is provided in the following
three figures. The pres-sure distribution near the mid-line of the
inner section(with the shorter flap, see Fig. 1) is shown in Fig.
11.
Figure 10. Polar description (with Cp=0 on the circular tire
outline) of the pressure coefficient along the rear wheel
centerline.
Figure 11. Pressure distribution along an inner section (with
the shorter flap) of the front wing.
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6The shape of the pressure distribution in Fig. 11
followscurrent design trends with a large laminar portion on
thewings suction (lower) side. In this particular
computation(without the turbulence model) a laminar bubble seems
toform behind the leading edge, creating the wavy shape inthe Cp
curve near the leading edge. The rear flap showssimilar trends and
some visible trailing edge separationas well. It is believed that
in the high-speed (over 100mph) and turbulent flow case, those
laminar bubbles nearthe leading edge will disappear.
Figure 12. Pressure distribution along an outer section (with
the longer flap) of the front wing.
Figure 13. Pressure distribution along the centerline of the
rear wing.
A similar pressure distribution diagram, but along anouter
section (placed near the tip, at the center of thelarger flap) is
shown in Fig. 12. In this case the flow onthe main element is
attached, but partially separated onthe flap. The shape of the
pressure distribution in thesetwo figures indicates a careful and
well-balanced airfoil
design for the front wing. The trailing edge flap angle forthis
particular condition, seems to be set at a too highvalue and the
shown gap between the two elements isprobably too large. The
interaction between the mainwing plane and its flap may be improved
by closing thegap somewhat.The rear wing pressure distribution is
presented in Fig.13. In this case, the INDY-car regulations force
the use ofa very long airfoil chord, resulting in a non-airplane
likepressure distribution. The suction peak at the front is
typ-ical to most airfoils at larger angles of attack; however,the
second suction peak at the aft section of the mainelement is less
traditional. This is a result of the sharpturn of the streamlines
near the gap region, causing alocal trailing edge separation. The
flap, in this case, too,is partially separated. This is standard
practice in searchof maximum rear downforce at the cost of
increasingrear-wing drag. The streamline plot, presented in Fig.
14,visualizes the flow in the symmetry plane of the rearwing. The
small trailing edge separation at the base ofthe main wing element
is hardly visible in this gray-scaleimage, but the separation of
the rear flap is more pro-nounced. These flow separations are
amplified by theabsence of the turbulence model, but traces of it
weredetected during full scale testing (by using tufts).
Figure 14. Streamlines released near the symmetry plane of the
rear wing.
CONCLUSIONS
The numerical model used in this study demonstrates
thefeasibility of solving the Navier-Stokes equations for acomplex
race car configuration within practical time limits.Computed
results clearly demonstrate the ability to simu-late viscous flow
separation on the complex componentsof open-wheel race cars (e.g
the flow over rotatingwheels). When properly used, this approach
can providethe reasoning for planned model modifications. It can
beused to propose and numerically test numerous wing
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7shapes and to virtually investigate various ideas
beforebuilding a test model. Numerical results may be used in
acomplementary manner with other experimental tech-niques because
of the easily available pressure distribu-tion and flow orientation
information, particularly in areasnear the wings, under the car and
near the rotatingwheels.
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