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7/18/2019 Fluent-Adv Turbulence 15.0 L02 Rans Models
http://slidepdf.com/reader/full/fluent-adv-turbulence-150-l02-rans-models 1/46
1 © 2014 ANSYS, Inc. April 23, 2014 ANSYS Confidential
Lecture 2:
RANS Turbulence Models in A
Turbulence Modeling Using A
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Overview
• RANS models in ANSYS-Fluent
–
Spalart-Allmaras model – k -e family of models
– k -w family of models
• Includes transition models (covered in L-3)
• Includes SAS model (covered in L-4)
–Reynolds stress models
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Turbulence Models Available in ANSYS F
RANS based
models
One-Equation Model
Spalart-Allmaras
Two-Equation Models
Standard k –ε
RNG k –ε
Realizable k –ε
Standard k –ω
SST k –ω
4-Equation v2f *
Intermittency Transition Modelk –kl –ω Transition Model
Transition SST Model
Reynolds Stress Model
Scale-Adaptive Simulation
Detached Eddy Simulation
Large Eddy Simulation
Comp
P
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Spalart-Allmaras Model Equations
Modified turbulent viscosity
normal dist
the wall
damping functio
2
1
2
2~
1
~
~~
~1~~
~
d f c
xc
x xS c
Dt D ww
j
b
j j
b
~,,~
3
1
3
3
11t
cv
vv f f
1
2222 11,
~~
v
vv f
f f d
S S
22
6
2
6/1
6
3
6
6
3~
~,g,
1
d S r r r cr
g g f w
w
ww
cc
0~: conditionboundaryWall
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Default definition uses rotation rate tensor only:
Alternative formulation also uses strain rate tensor:
− reduces turbulent viscosity for vortical flows
− more correctly accounts for the effects of rotation
Spalart-Allmaras Production Term
i
j
j
i
xU
xU S
ijijij 2
1;2
)-min(0, ijij prodij S C S
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Spalart-Allmaras Model• Spalart-Allmaras model developed for unstructured codes in
aerospace industry
–
Increasingly popular for turbomachinery applications – “Low-Re” formulation by default
– can be integrated right down to the viscous sublayer
– Fluent’s implementation can also use the wall function (law of the wal
– Economical and accurate for:
– wall-bounded flows
–
flows with mild separation and recirculation
– Weak for:
– massively separated flows
– free shear flows
– simple decaying turbulence
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Two-Equation Models
• Two transport equations are solved, giving two independfor calculating
t
–
Virtually all use the transport equation for the turbulent kinetic – Several transport variables have been proposed, based on dime
arguments, and used for second equation
– Kolmogorov, w :
t k /w
l
k 1/2 / w k e / w
•w
is specific dissipation rate
• defined in terms of large eddy scales that define supp
– Chou, e :
t k 2 / e l k 3/2 / e
– Rotta, l :
t k 1/2 l e k 3/2 / l
– Boussinesq relation still used for Reynolds Stresses
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e e e
e e e
e 2
2t1
t C S C k x x Dt
D
j j
Standard k -e Model Equations
production dissipation
inverse time scale
Empirical constants determined from benchmar
experiments of simple flows using air and water
k – transport equation
e
transport equation
coefficients
Finally, turbulent viscosity
ijijt jk j S S S S x
k
x Dt
Dk
2;
2t
e
2,,, e e e C C ik
e
2
k
C t
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Closure Coefficients
• Simple flows render simpler model equations
– Coefficients can be isolated and compared with experiment
–e.g.,
• Uniform flow past grid
– Standard k -e equations reduce to just convection and dissipati
• Homogeneous Shear Flow
• Near-Wall (Log layer) Flow
k
C
x
U
x
k U
2
2
d
d;
d
d e e e e
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• High-Reynolds number model
– (i.e., must be modified for the near-wall region)
• The term “standard” refers to the choice of coefficie
• Sometimes additional terms are included
– production due to buoyancy
• unstable stratification (g·T > 0) supports k production
–
dilatation dissipation due to compressibility• added dissipation term, prevents overprediction of spreading rate in com
Buoyancy
production
Di
Dis
x g S
x
k
x Dt
Dk
it
t it
jk
t
j
2Pr
2
e
Standard k -e Model
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Standard k -e Model Pros & Cons
• Strengths:
– robust
–
economical – reasonable accuracy for a wide range of flows
• Weaknesses:
– overly diffusive for many situations• flows involving strong streamline curvature, swirl, rotation, separating flows,
–
cannot predict round jet spreading rate
• Variants of the k -e model have been developed to addresdeficiencies
– RNG and Realizable
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RNG k -e Model Equations
• Derived using renormalization group theory
– scale-elimination technique applied to Navier-Stokes equatequations to specific flow regimes)
• k – equation is similar to standard k -e model
• Additional strain rate term in e - equation
– most significant difference between standard and RNG k -e models
• Analytical formula for turbulent Prandtl numbers
• Differential-viscosity relation for low Reynolds numbers
– Boussinesq model used by default
wheree e e
e
e e e
*
2
2
1eff C S C
k x x Dt
Dt
j j
t
k S
C
C C
eff
0
2
*
2
,
e
e e
coeare
e transport equation
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RNG k -e Model Pros & Cons
• For large strain rates:
– where > 0 e is augmented, and therefore k and
t are
• Option to modify turbulent viscosity to account for
• Buoyancy and compressibility terms can be included
• Improved performance over std. k -e model for
–
rapidly strained flows – flows with streamline curvature
• Still suffers from the inherent limitations of an isotrviscosity model
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Realizable k -e Model: Motivation
• Standard k -e model could not ensure:
– Positivity of normal stresses
– Schwarz’s inequality of shear stresses
• Modifications made to standard model
– k − equation is same; new formulation for t and e
– C
is variable
– e − equation is based on a transport equation for the mean
vorticity fluctuation
02 u
uuuu 22
2
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Realizable k -e Model: Realizability
• How can normal stresses become negative?
– Standard k -e Boussinesq viscosity relation:
– Normal component:
– Normal stress will be negative if:
3
2 -
2
ij
i
j
j
i
ji k x
U
x
U k C uu
e
23
2
22
x
U k
C k u
e
3.73
1
e C x
U k
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Realizable k -e Model: C
• C
is not a constant, but varies as a function of mean velocity field and
(0.09 in log-layer S k / e = 3.3, 0.05 in shear layer of S k / e = 6)
C
contours for 2D backward-facing step
C
along bottom-w
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Realizable k -e Model Equations
where
e transport equation
turbulent viscosity
e
e e
e
e
e
k
C S C
x x Dt
D
j
t
j
2
21
0.1 ,/,5
,43.0max 21
C k S C e
e e
k U A A
C k
C
s
t *
0
2
1,
W A A s 6cos3
1,cos6,04.4 1
0
ijij
ki jk ij
ijijijij S S S
S
S S S W S S U
~,~ ,*
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Realizable k -e Model Pros & Cons
• Performance generally exceeds the standard k -e mo
• Buoyancy and compressibilty terms can be included• Good for complex flows with large strain rates
– recirculation, rotation, separation, strong
P
• Resolves the round-jet/plane jet anomaly
–
predicts the spreading rate for round and plane jets
• Still suffers from the inherent limitations of an isotroeddy-viscosity model
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Standard and SST k -w Models
• k-w models are a popular alternative to k -e
– w ~ e / k
–
t k / w
• Can be used in the near-wall region without modificatio
• Wilcox’s original model was found to be quite sensitive tfar-field boundary values of w
• Latest version contains several refinements: – reduced sensitivity to boundary conditions
– modification for the round-jet/plane-jet anomaly
– compressibility effects
– low-Re (near wall) effects
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Standard k -w
Model
• Standard k -w model in Fluent is Wilcox’ 1998 model
j
t
j j
i
ij
jk
t
j j
iij
t
x x f
x
U
k Dt
D
x
k
xk f
x
U
Dt
Dk
k
w
w
w
w
w
w
w
2
*
*
*
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Standard k -w
Turbulent Viscosity
• Turbulent viscosity is computed from:
• The dependency of * upon ReT was designed to recovecorrect asymptotic values in the limiting cases. In particu
that:
w
k t
*
0.1 ,Re,6
125
9,
3,
Re1
Re
*
*
0
*
0**
w
k R
R
R
T k
ii
k T
k T where
turbulent(fully T Reas1*
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Standard k -w Turbulent Kinetic Energ
• Note the dependence upon ReT , M t , andk
• “Dilatation” dissipation is accounted for via M t term
• The cross-diffusion parameter ( k
) is designed to improve free shea
k of Diffusionk of ratenDissipatio
*
k of production
*
jk
t
j j
iij
x
k
xk f
x
U
Dt
Dk
w
09.0 ,5.1 ,0.2
8,Re1
Re154
1
**
4
4
**
***
k
T
T
i
t i
R R
R
M F
d-cross
k
k
k
k
k
t t
t t t t
t t
t
f
RT a M a
k M
M M M M
M M M F
2
2
02
2
0
2
0
2
0
,0
4001
6801
01
,4
1,
2
0
*
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Standard k -w Specific Dissipation Equa
• Note the dependence upon ReT , M t , and
w
• Vortex-stretching parameter (w
) designed to remedy the plane/rou
j
t
j j
iij
x x
f
x
U
k Dt
D w
w
w
w
w
2
i
j
j
iij
i
j
j
iij
ki jk ij
t
i
ii
T
T
xU
xU
xU
xU S
S f M F
R R
R
*
3*
**
00
*
21,
21
5.1 ,,801
701,1
0.2,95.2,9
1,
25
13,
Re1
Re
w
w
w
w
w w
w
w
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Standard k -w Sub-models & Options (• “Low-Re Corrections” option – Corresponds to all terms involving ReT
terms in the model equations
–Deactivated by default
– Can benefit low-Re flows where the meshcan support good near-wall resolution
• “Compressibility Effects” option – Takes effects via F(Mt )
–
Accounts for “dilatation” dissipation
k k
k d d s
x
u
x
u
e e e e
3
4,
– Available with ideal-gas option only and is turned off by defaul
– Improves predictions for high-Mach number free shear flows −
reduces sprea
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Standard k -w Sub-models & Options (
• “Shear-Flow Corrections” option – activated by default
Controls both cross-diffusion and vortex-stretching terms
–
Cross-diffusion term (in k − equation)
• Designed to improve the model performance for free shear flows without afflayer flows
–Vortex-stretching term• Designed to resolve the round/plane-jet anomaly
• Takes effects for axi-symmetric and 3-D flows but vanishes for planar 2-D flo
3*,
801
701
w
w
w
w
ki jk ij S
f
parameter diffusion-cross
j j
k
k
k
k
k
x x
k f
w
w
3
2
21
,0
4001
6801
01
*
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Menter’s SST k -w
Model: Background
• Many people, including Menter (1994), have noted
– Wilcox’ original k -w model is overly sensitive to the freestr
value (BC) of w, while k -e model is not prone to such probl
– The k -w model has many good attributes and performs mu
better than k -e models for boundary layer flows
– Most two-equation models, including k -e models, over-pre
turbulent stresses in the wake (velocity-defect) region, whto poor performance of the models for boundary layers un
adverse pressure gradient and separated flows
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Menter’s SST k -w Model: Main Compon
• The SST k -w model consists of
– Zonal (blended) k -w / k -e equations (to address item 1 and 2
previous slide)
– Clipping of turbulent viscosity so that turbulent stresses sta
is dictated by the structural similarity constant. (Bradshaw,
addresses item 3 in the previous slide
Inner layer
(sublayer, log-layer) Wilcox’ original k-w model
e
e
23
k
Wall
Outer layer (wake and
outward)
k -w model transformed
from standard k -e model
Modified Wilcox k -w model
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Menter’s SST k -w
Model: Inner Layer
• The k -w model equations for the inner layer are tak
Wilcox original k -w
model with some constants mo
j
t
j j
iij
t
jk
t
j j
iij
x x x
U
Dt
D
x
k
xk
x
U
Dt
Dk
w
w
w
w
w 1
2
11
1
*
41.0,,09.0
0.2,176.1,075.0
1
*2*
11
*111
w
w k
w
w
w
22
2
22
21
1
500,
09.0
2maxarg,argtanh
,amax
y y
k F
F
k at
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Menter’s SST k -w
Model: Outer Layer
• The k -w model equations for the outer layer are obtainetransforming the standard k -e equations via change-of-v
• Turbulent viscosity computed from:
j j
j
t
j j
iij
t
jk
t
j j
iij
x x
k
x x x
U
Dt
D
x
k
xk
x
U
Dt
Dk
w
w
w
w
w
w
w
w
12 2
2
2
22
2
*
41.0,,09.0
168.1,0.1,0828.0
2
*2*
22
*
222
w
w k
w k
t
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Menter’s SST k -w: Blending the Equatio
• The two sets of equations and the model constants are blended in su
the resulting equation set transitions smoothly from one equation to
*1
1
2max
maxminarg
tan
k CD
k
F
w
ww
w ,,,where
1
1
2111
outer
1
inner
1
k
F F
Dt Dk F
Dt Dk F
in
in
0
1
1
1
F
F Wilcox’ original k-w model
e
e
23
k
Wall
k-w model transformedfrom std. k-e model
Modified Wilcox k-w model
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Menter’s SST k -w: Blended k -w Equatio
• The resulting blended equations are:
Wall
j j
j
t
j j
iij
t
jk
t
j j
iij
x x
k F
x x x
U
Dt
D
x
k
x
k
x
U
Dt
Dk
w
w
w
w
w
w
w
w
112
21
2
*
w ,,,,1 2111 k F F
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Menter’s SST k -w: Turbulent Viscosity• Honors the “structural similarity” constant for boundary layer
(Bradshaw, 1967)
• Turbulent stress implied by turbulence models can be written
– In many flow situations (e.g. adverse pressure gradient flows), production TKE can be much larger than dissipation ( P k >> e ), which leads to predicteturbulent stress larger than what is implied by the structural similarity con
– Turbulent stress can be limited by clipping the turbulent viscosity such tha
1967(Bradshaw,11 ak
vuk avu
ε
P k a
y
U k t t 1
k at 1
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Menter’s SST k -w
Model Clipping t
• Turbulent viscosity for the inner layer is computed f
• Remarks – F
2 is equal to 1 inside boundary layer and goes to zero far from the wall an
shear layers
– The name SST (shear-stress transport) originates from this
– Note that the vorticity magnitude is used (strain-rate magnitude could also
magnitude)(vorticity2
500,
09.0
2maxarg,argtanh
,min,amax
22
2
22
2
1
21
1
ijij
t
y y
k F
F
k ak
F
k a
w
w
w
w
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Menter’s SST k -w: Submodels & Optio• SST k -w model comes with: – Low-Re Corrections option
(Off by default)
–
Compressibility Effects option when ideal-
gas option is selected
(Off by default)
• The original SST k -w model in theliterature does not have any of these
options – These submodels are being borrowed from
Wilcox’ 1998 model - should be used withcaution
– Do not activate any options to recover theoriginal SST model
d l d d
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k -w Models: Boundary Conditions
• Wall boundary conditions – The Enhanced Wall Treatment (EWT) is the sole near-wall optio
models. Neither the standard wall functions option nor the non
equilibrium wall functions option is available for k-w models inFluent• The blended laws of the wall are used exclusively
• w values at wall adjacent cells are computed by blending the wall-limiti→ 0 ) and the value in the log-layer
– The k -w
models can be used with either a fine near-wall mesh onear-wall mesh
• For other BCs (e.g., inlet, free-stream), the following relais used internally, whenever possible, to convert to and fdifferent turbulence quantities:
09.0, ** w e k
d l &
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k -w Models: Pros & Cons
• Use of w instead of e allows for better resolution of bounlayers, especially under adverse pressure gradients
• The Standard k-w model is sensitive to inlet and far field – The SST k-w model does not suffer from this
• Sometimes more difficult to converge than any of the k-e
• The best RANS models for wall bounded aerodynamic flo
airfoils, compressors, turbines, and flows with separationadverse pressure gradient
– Use SST to prevent boundary condition sensitivity
• Often the best models for heat transfer predictions
F lt i th B i A ti
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Faults in the Boussinesq Assumption
• Boussinesq: R i j = 2 tS i j
– Is simple linear relationship sufficient?
• R i j is strongly dependent on flow conditions and history
• R i j changes at rates not entirely related to mean flow processes
– R i j is not strictly aligned with S i j for flows with:
• sudden changes in mean strain rate
• extra rates of strain (e.g., rapid dilatation, strong streamline curv
• rotating fluids
• stress-induced secondary flows
• Modifications to two-equation models cannot be generaarbitrary flows
R ld St M d l
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• Starting point is the exact transport equations for th
transport of Reynolds stresses, R ij
–
six transport equations in 3D
• Equations are obtained by Reynolds-averaging the p
of the exact momentum equations and a fluctuating
• The resulting equations contain several terms that mmodeled
0)()(
i j ji u NS uu NS u
Reynolds Stress Models
Reynolds Stress Transport Equations
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Reynolds Stress Transport Equations
k
ijk
ijijij
ij
x
J P
Dt
DR
e
Generation
k
ik j
k
j
k iij x
U uu
x
U uu P
i
j
j
iij
x
u
x
u p
k
j
k
iij
x
u
xu
e 2
Pressure-Strain
Redistribution
Dissipation
Turbulent
Diffusion
(modeled)
(related to e)
(computed)
(incompressible fl
forces)
Reynolds Stress
Transport Eqns.
( ji
k
k jiik j jk iijk uu x
uuuu pu p J
Pressure/velocity
fluctuations
Turbulent
transport
Molecular
transport
Di i ti M d li
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• Dissipation rate is predominantly associated with sm
eddy motions
–
Large scale eddies affected by mean shear – Vortex stretching process breaks eddies down into continual
scales
• The directional bias imprinted on turbulence by mean flow is gradually lo
• Small scale eddies assumed to be locally isotropic
•e
is calculated with its own (or related) transport equation
• Compressibility effects can be included
Dissipation Modeling
e e ijij3
2
Turbulent Diffusion
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Turbulent Diffusion
• Most closure models combine the pressure diffusion
triple products and use a simple gradient diffusion h
– Overall performance of models for these terms is generally i
based on isolated comparisons to measured triple products
– DNS data indicate that above p terms are negligible
lk s
k
ji
k
jik ikjk ji
k uu
k C
xuu
xuu
puuu
x e
'
k
k C
x e
2
Or even a simpler model
Pressure Strain Modeling
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Pressure-Strain Modeling• Pressure-strain term of same order as production
• Pressure-strain term acts to drive turbulence towards an
isotropic state by redistributing the Reynolds stresses• Decomposed into parts
• Model of Launder, Reece & Rodi (1978)
i
j
j
i
i
j
i
ii x
u
x
u
x
uu
x x
p
21
ij
m
l ml
l
il j
l
j
l iijij x
U uu
x
U uu
x
U uucbc
3
221
i
j
i
ii x
U
x
u
x x
p
2
1 2
“Rapid” Part “Slow” Part
ijbwhere
wijijijij ,2,1,
ij p
Pressure Strain Modeling Options
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Pressure-Strain Modeling Options
• Wall-reflection effect
– contains explicit distance from wall
–
damps the normal stresses perpendicular to wall – enhances stresses parallel to wall
• SSG (Speziale, Sarkar and Gatski) Pressure Strain Mo
–
Expands the basic LRR model to include non-linear (quadrati – Superior performance demonstrated for some basic shear flo
• plane strain, rotating plane shear, axisymmetric expansion/contr
Stress Model
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Stress-w Model
• Uses the w equation from the standard k -w model rae
from the k -e model
• Selecting “Low-Re Corrections” in the viscous modelafter selecting “Stress-Omega” activates the same teactivated in the standard k -w model and also low Remodifications of the pressure strain model
• Potentially beneficial compared to other RSM optionwhere the viscous sublayer must be resolved in ordeproduce an accurate solution
– Predictions of k -w models are generally superior to those ofsuch flows
Characteristics of RSM
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Characteristics of RSM
• Effects of curvature, swirl, and rotation are directly a
for in the transport equations for the Reynolds stres
–
when anisotropy of turbulence significantly affects the meanconsider RSM
• More cpu resources (vs. k -e models) is needed
–
50-60% more CPU time per iteration and 15-20% additional m
• Strong coupling between Reynolds stresses and the
– number of iterations required for convergence may increase
Heat Transfer
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Heat Transfer
• The Reynolds averaging process produces an additio
in the energy equation: (q
is the fluctuating co
of static temperature) – Analogous to the Reynolds stresses, this is called the turbule
• It is possible to model a transport equation for the heat flux, but
common practice
• Instead, a turbulent thermal diffusivity is defined proportional to
turbulent viscosity – The constant of proportionality is called the turbulent Prandtl
– Generally assumed that Pr t ~ 0.85-0.9
• Applicable to other scalar transport equations
q iu