04 turbulence
TRANSCRIPT
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Turbulence and Fluenturbulence and Fluent
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Turbulence Modeling
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What is Turbulence?
We do not really know
3D, unsteady, irregular motion in which transported quantitiesfluctuate in time and space. Turbulent eddies (spatial structures). Diffusive (mixing).
Self-sustaining if a mean shear exist. Entrainment.
Energy cascade. Energy is added at the large eddies. Energy is dissipated at the small eddies.
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Turbulent Flows
LargerStructures
SmallerStructures
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Computational Approaches
DNS (Direct Numerical Simulation) Solves the Navier-Stokes (N-S) equations. No turbulence modeling required. Not practical for industrial flows (requires Low Re and simple geometries).
LES (Large Eddy Simulation) Solves a filtered version of the N-S equations. Less expensive than DNS, but still too expensive for most applications.
RANS (Reynolds-Averaged N-S) Solve the ensemble-averaged N-S equations. All turbulence is modeled. The most widely used approach for calculating industrial flows.
There is not yet a single turbulence model that can reliably predict allturbulent flows found in industrial applications with sufficient accuracy.
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Computational Approaches 2)
LES, DNS
RANS
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RANS Modeling
Reynolds decomposition:
The Reynolds-averaged momentum equations are as follows:
where is called the Reynolds stresses . The Reynolds stressesmust be modeled to close the equations.
j
ij
j
i
jik
ik
i
x
R
x
U
x x
p
x
U U
t
U
+
+
=
+
jiij uu R =
( ) ( ) ( )t xut xU t xu iii ,,, rrr +=
Turbulentfluctuation
Mean
u' i
U i ui
time
u
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The Closure ProblemReynolds equations does not contain enough equations to solve for all the
uknown variables. Thus, the Reynolds stresses must be modeled.
Modeling approaches Eddy-Viscosity Models (EVM):
Boussinesq hypothesis: Reynolds stresses are modeled using an eddy (orturbulent) viscosity t . Assumes Isotropic turbulence.
Reynolds-Stress Models (RSM): solves transport equations for all individual Reynolds stresses. Require modeling for many terms in the Reynolds stress equations. Does NOT assume isotropic turbulence.
ijijk
k
i
j
j
i jiij k x
U xU
xU uu R
32
32 tt
+==
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Modeling the Eddy Viscosity
Basic approach made through dimensional arguments Units of t = t/ are [m 2/s] Typically one needs 2 out of the 3 scales:
velocity - length - time
Commonly used scales is the turbulent kinetic energy [L2/T2]
is the turbulence dissipation rate [L2/T3] is the specific dissipation rate [1/T]
Models classified in terms of number of transport equations solved,
zero-equation models one-equation models two-equation models
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Spalart-Allmaras A one-equation RANS model
A low-cost model solving an equation for the modified eddy viscosity
Eddy-viscosity is obtained from
Mainly for aerodynamic/turbo-machinery applications with mild separation(supersonic/transonic flows over airfoils, boundary-layer flows, etc).
( )( ) 31
3
3
11/~
/~,~
v
vvt C
f f +
=
~
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Standard k SKE A two-equation RANS model
Transport equations for k and :
The most widely-used engineering turbulence model for industrialapplications
Robust Performs poorly for flows with strong separation, large streamline
curvature, and large pressure gradient.
( )
( )k
C Gk
C x x Dt
D
G xk
xk Dt D
k e j
t
j
k jk
t
j
2
21
+
+
=
+
+
=
3.1,0.1,92.1,44.1,09.0 21 ===== k C C C where
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k m o els
+
+
=
+
+
=
=
j
t
j j
iij
jk
t
j j
iij
t
x x f
xU
k Dt D
x
k
xk f
x
U
Dt
Dk
k
2
*
*
*
1
k
specific dissipation rate:
Two-equation RANS models
Fluent supports the standard k- model by Wilcox (1998), and Menters SST k- model (1994).
k- models are inherently low-Re models: Can be integrated to the wall without using any damping functions Accurate and robust for a wide range of boundary layer flows with pressure
gradient Most widely adopted in the aerospace and turbo-machinery communities. Several sub-models/options of k- : compressibility effects, transitional flows
and shear-flow corrections.
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Reynolds-Stress Model RSM)
( ) ( ) ijijT ijijij jik k
ji DF PuuU xuu
t +++=
+
Turbulent diffusionStress-production
Rotation-productionPressure strain
Dissipation
Modeling required for these terms
Attempts to address the deficiencies of the EVM. Anisotropy, history effects of Reynolds stresses. RSM requires more modeling (the pressure-strain is most critical and difficult
one among them). More expensive and harder to converge. Most suitable for complex 3-D flows with strong streamline curvature, swirl and
rotation.
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Near Wall Modeling
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The Structure of Near-Wall
Flows The structure of turbulent boundary layers in the near-wall region:
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Near-Wall Modeling
Wall Functions Wall Integration
Accurate near-wall modeling isimportant to correctly predict frictionaldrag, pressure drop, separation, heat
transfer etc.
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Placement of The First Grid
Point For standard or non-equilibrium wall functions, each wall-adjacent
cells centroid should be located within:
For the enhanced wall treatment (EWT), each wall-adjacent cellscentroid should be located: Within the viscous sublayer, , for the two-layer zonal model:
Preferably within for the blended wall function
How to estimate the size of wall-adjacent cells before creating the grid: , The skin friction coefficient can be estimated from empirical
correlations:
2// f ew cU u =
30030 + p y
1+ p y
u y yu y y p p p p // ++
30030 +
p y
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Near-Wall Modeling:
Recommended Strategy Use SWF or NWF in high Re applications (Re > 10 6) where you
cannot afford to resolve the viscous sub-layer. Use NWF for mildly separating, reattaching, or impinging flows.
You may consider using EWT if:
Near wall characteristics are important. The physics and near-wall mesh of the case is such that y + is
likely to vary significantly over a wide portion of the wall region.
Try to make the mesh either coarse or fine enough to avoid placingthe wall-adjacent cells in the buffer layer (y + = 5 ~ 30).
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Enhanced Wall Treatment
Fully-Developed Channel Flow ( Re t = 590)
For fixed pressure drop cross periodic boundaries, different near-wall mesh resolutions yielded different volume flux as follows
The enhanced near-wall treatment gives a much smaller variationfor different near-wall mesh resolutions compared to the variationsfound using standard wall functions.
y+ = 1 y + = 4 y + = 8 y + = 16
Std. W all fn. 12.68 13.77 16.77 19.08
EW T 18.31 17.58 17.70 18.48
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Inlet/Outlet Conditions
Boundary conditions for k, , w and/or must be specified.
Direct or indirect specification of turbulence parameters:
Explicitly input k, , w, or This method allows for profile definition.
Turbulence intensity and length scale
For boundary layer flows: l 0.4 d99 For flows downstream of grid: l opening size
Turbulence intensity and hydraulic diameter
Internal flows Turbulence intensity and turbulent viscosity ratio For external flows: 1 < m t/m < 10
jiuu
jiuu
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Is the Flow Turbulent?
External Flows
Internal Flows
5
105 x Re along a surface
around an obstacle
,3002h D
Re
UL
Re L where
L = x, D , D h, etc.
20,000 D Re Other factors such as free-streamturbulence, surface conditions, anddisturbances may cause earliertransition to turbulent flow.
Natural Convection
3TLg
Ra where108 1010 Ra
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f b l d l
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GUI for Turbulence Models
Define Models Viscous...
Turbulence Model options
Near Wall Treatments
Inviscid, Laminar, or Turbulent
Additional Turbulence options
RANS Turbulence Model
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RANS Turbulence ModelBehavior and Usage
Model Behavior and Usage
Spalart-Allmaras
Standard k -
RNG k -
Realizable k -
Standard k -
SST k
-
RSM
Economical for large meshes Performs poorly for 3D flows, free shear flows, flows with strong separation Suitable for mildy complex (quasi-2D) flows (turbo, wings, fuselages, missilies)
Robust, but performs poorly for complex flows Suitable for initial conditions, fast design screening and parametric studies
Suitable for complex shear flows involving rapid strain, moderate swirl, vortices,locally transitional flows (e.g. b.l. Separation, massive separation, vortex shedding)
Similar benefits and applications as the RNG model Possibly more accurate and easier to converge
Superior for wall-bounded, free shear, and low-Re flows Suitable for complex b.l flows (e.g. external aero, turbomachinery, vortex shedding) Can predict transition (usually predict to early transition, though)
Similar benefits as SKO, less sensitive to outer disturbances Suitable for wall bounded flows, less suited for free shear flows
The most physically sound RANS model (handels anisotrophy) Computationally expensive and harder to converge Suitable for complex 3D flows with strong streamline curvature, strong swirl(e.g. Curved duct, swirl combustors, cyclones)
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Examples
H t T f B hi d 2D
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Heat Transfer Behind a 2D
Backstep Heat transfer predictions along the bottom Measured by Vogel and Eaton (1980)
SKE, RNG, and RKE models are employed with standard wallfunctions.
Factors affecting
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Factors affecting
accuracy The accuracy of turbulent flow predictions can be
affected by user decisions involving Turbulence model Boundary conditions Grid resolution and near wall modeling
Grid quality
I t f T b l M d l
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Impact of Turbulence Model
k- Results
Impact of Boundary Conditions
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Impact of Boundary Conditions
RunX-Velocity
B.C.Thermal
B.C. Turbulence B.C.
1 Profile Uniform
Uniform
Uniform
Profile
2 Uniform Intensity & Hydraulic
Diameter 3 Profile k=1, =1
Impact of Grid Quality
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Impact of Grid Quality
Structured
Tri w b/l
Quad Pave
Tri
Impact of Near Wall Modeling
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Impact of Near Wall Modeling
y+ values must be appropriate for selected near wall treatment Realizable k- with SWF
Stream Function Contours for
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Stream Function Contours for180 Degree Bend
Spalart-Allmaras Standard k-
RNG k- RSM
Rotating Flow in a Cyclone
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Rotating Flow in a Cyclone
0.2 m
0.97 m
0.1 m
Uin = 20 m/s
0.12 m
Highly swirling flows ( Wmax= 1.8 Uin)
High-order discretization on40,000 cell hexahedralmesh
Computed using a family ofk- models (SKE, RNG,RKE), k- models (Wilcox,
SST) and RSM models
Cyclone Velocity Profiles
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Cyclone Velocity Profiles