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2
Introduction
CV, or integral, forms of equations are useful fordetermining overall effects.
However, detailed knowledge about the flow fieldinside the CV cannot be obtain. (motivation for
differential analysis)Application of differential equations of fluid
motion to any and every point in the flow field or
flow domain
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3
Description of fluid motion
FLUID KINEMATICS - the study of how fluids flowand how to describe fluid motion.
There are two distinct ways to describe motion.
Lagrangian description of fluid motion: Individual
objects or individual fluid particles are tracked (function of
time) as they move through the flow field.
Eulerian description of f luid f low:A finite volume called a
flow domain or control volume (CV) is defined, throughwhich fluid flows in and out and a track of the position and
velocity of a mass of fluid particles is not made. Instead,
field variables, are defined as functions of space and time,
within the control volume.
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4
Description of fluid motion
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Lagrangian Description
Named after Italian mathematician Joseph LouisLagrange (1736-1813).
Lagrangian description of fluid flow tracks theposition and velocity of individual particles.
Based upon Newton's laws of motion. Difficult to use for practical flow analysis.
Fluids are composed ofbillions of molecules.
Interaction between molecules hard to describe/model.
However, useful for specialized applications
Sprays, particles, bubble dynamics, rarefied gases.
Coupled Eulerian-Lagrangian methods.
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Eulerian Description
Named after Swiss mathematician Leonhard Euler (1707-1783).
Eulerian description of fluid flow: a flow domain or control
volume is defined by which fluid flows in and out.
Field variables are define which are functions of spaceand time.
Velocity,
Acceleration,
These (and other) field variables define the flow field.
Well suited for formulation of initial boundary-value
problems (PDE's).
, , , , , , , , ,V u x y z t i v x y z t j w x y z t k
, , , , , , , , ,
x y z
a a xyzt i a x yzt j a xyzt k
, , ,a a x y z t
, , ,V V x y z t
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Conservation of Mass (Differential CV & Taylor series)
Infinitesimal CV
of dimensions
dx, dy, dzArea of right
face = dy dz
Mass flow rate through
the right face of the
control volume
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Conservation of Mass (Differential CV & Taylor series)
Now, sum up the mass flow rates into and out ofthe 6 faces of the CV
Plug into integral conservation of mass equation.
After substitution,
Net mass flow rate into CV:
Net mass flow rate out of CV:
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Conservation of Mass (Differential CV & Taylor series)
Dividing through by volume dxdydz
Or, if we apply the definition of the divergence of a vector
Use product rule on divergence term
orWhere, D/Dt is
material or total
derivative
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Total or Material derivative The total derivative operator (d/dt) is also given special notation,
D/Dt.
Remember D/Dt (or d/dt) and /t are physically and numericallydifferent quantities, The former is the time rate of change
following a moving fluid particle while later is the time rate ofchange at fixed location.
Provides ``transformation'' between Lagrangian and Eulerianframes.
Other names for the material derivative include: total, particle,
Lagrangian, Eulerian, and substantial derivative. It can be applied to any fluid properties, both scalars and vectors
(e.g. V, , p etc.). For example, the material derivative of
velocity & pressure can be written as:
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Conservation of Mass (Cylindrical coordinates)
In general, continuity equation cannot be used by
itself to solve for flow field, however it can be used to:
1. Determine if velocity field is incompressible.
2. Find missing velocity component.
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Conservation of Mass (Special Cases)
Cartesian
Cylindrical
Incompressible flow: = constant
Steady compressible flow:
0
Also D/Dt =0
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Where n is unit normal vector. By applying Gauss
divergence theorem , volume integral of divergence of
vector can be equated to area integral over the surface that
defines the volume,
Continuity Equations - integral
SV
ndSVdVdtd .
SV
ndSVdVVdivdt
d. 0)(
V
dVVt
Any size of volume, V 0)(
Vt
Mass conservationequation
In Cartesian coordinate system, it
expressed as:
0
z
w
y
v
x
u
t
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Momentum Equation
Consider a fluid particle and Newton's second law,
Acceleration Field - The acceleration of the particle is the
time derivative of the particle's velocity.
However, particle velocity at a point is the same as the fluid
velocity,
To take the time derivative of, chain rule must be used.
particle particle particleF m a
particleparticle
dVa
dt
, ,particle particle particle particleV V x t y t z t
particle particle particle
particle
dx dy dzV dt V V V a
t dt x dt y dt z dt
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Acceleration Field
Since
In vector form, the acceleration can be written as
The total or material derivative operator d/dt ( or D/Dt)
emphasize that it is formed by following a fluid particle as it
moves through the flow field.
First term is called the local acceleration and is nonzeroonly for unsteady flows.
Second term is called the advective acceleration and
accounts for the effect of the fluid particle moving to a new
location in the flow, where the velocity is different.
, , , dV V
a x y z t V V dt t
particle
V V V V a u v w
t x y z
, ,particle particle particledx dy dz
u v w
dt dt dt
.
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Momentum Equation
The Newton's second law application to differential fluid
element in a CV is given by:
Total forces on differential fluid element:
While body forces are analyzed by simple relation such as:
Surface forces are not as simple to analyze as above since
they consist of both normal and tangential components.
(1)
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Forces acting on CV consist of body forces that actthroughout the entire body of the CV (such as gravity,
electric, and magnetic forces) and surface forces that
act on the control surface (such as pressure and viscous
forces, and reaction forces at points of contact).
Body forces act on each
volumetric portion dV of
the CV.
Surface forces act on eachportion dA of the CS.
Momentum Equations
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Body Forces (gravity, electric and magnetic forces)
The most common body forceis gravity, which exerts a
downward force on every
differential element of the CV.
Total body force acting on CV:
The differential body force:
Typical convention is that
gravity acts in the negative
(e.g. z-direction):
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Surface Force Surface forces are not simple to analyze
as they include both normal & tangentialcomponents, i.e. the description of the
force in terms of its coordinate changes
with orientation.
Second-order tensor called the stress
tensorij is used in order to adequatelydescribe the surface stresses at a point
in the flow.
Diagonal components xx, yy zz are
called normal stresses and are due to
pressure and viscous stresses. Off-diagonal components xy, xz etc.,
are called shear stresses & are due
solely to viscous stresses.
Total surface force acting on CS:
Surface integrals are
cumbersome to solve
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Momentum Equation
For brevity, here we consider on only x-component of Totalforces acting on differential element to simplify the diagram.
Thus, the body force and the net surface force due to
stresses in the xdirection can be given as:
Combining equations above, equating to Total forces in x-
direction (eq. 1) & dividing by dxdydz becomes:
(2)
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Momentum Equation
Thus the differential forms for y and z- direction momentum
equations :
Or equations 1, 2, 3 & 4 are combine to give equationsbelow:Cauchys
Equation
(3)
(4)
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Momentum Equations (integral)
Body Force Surface Force ij = stress tensor
Substituting volume integrals gives,
Recognizing that this holds for any CV, the integral may be
droppedCauchys
Equation
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The Navier-Stokes Equation
As seen, Cauchy's equation is not useful in its present form, there are ten
(10) unknowns:
6 independent component of stress tensor (ij )
1 Density ()
3 independent Velocity components (V)
4 equations (continuity + momentum)
Thus in order to resolve flow field, 6 more equations are required to close
problem!
Thus,ij is separated into pressure and viscous stresses terms:
ijxx xy xz
yx yy yz
zx zy zz
p 0 00 p 0
0 0 p
xx xy xz
yx yy yz
zx zy zz
Viscous Stress Tensor
When fluid is at rest p acts & this p always
acts inward & normal to surface
When fluid is in motion p still acts inward &
but viscous stress may also exist
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The Navier-Stokes Equation
Situation not yet improved, 6 unknowns in ij 6
unknowns in ij & 1 in P, which means one more is added!Reduction in the number of variables is achieved by relating
shear stress to strain-rate tensor (as it can be related tovelocity and material property).
For Newtonian fluid with constant properties (e.g. & T =
const.).
Substituting Newtonian closure into stress tensor gives:
Using the definition of ij :
Shear strain rate can be expressed in Cartesian coordinatesas:
, ,xx yy zzu v w
x y z
1 1 1, ,
2 2 2xy zx yz
u v w u v w
y x x z z y
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The Navier-Stokes Equation Combine linear strain rate and shear strain rate into one
symmetric second-order tensor called the strain-rate tensor.
Upon Substitution:
Substituting ij into Cauchys equation below gives us the N-S
eqns:
(6)
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The Navier-Stokes Equation
Substitute equation (6) into three Cartesian coordinate of
Cauchy's equation (5), taking x-direction
Similar expression can be arrived for y and z directions.Also note that as long as velocity components are smooth
function, the order of differentiation is irrelevant, thus
This is from x-componentThis is from z-component
For Incompressible, the
term in parentheses =0
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The Navier-Stokes Equation
Thus equation becomes .. the Navier Stokes eqns:
This results in a closed system of equations!
4 equations (continuity and momentum equations)
4 unknowns (U, V, W, p)
Note: Above is unsteady, nonlinear, second order partial differential eqn.
Incompressible NSE
written in vector formAdvectionPressure gradient Body force Diffusion
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The Navier-Stokes Equation
Continuity
X-momentum
Y-momentum
Z-momentum
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The Navier-Stokes Equation
In the field of CFD, the conservation of mass, momentum,(and/or energy) equations are collectively referred to as
the Navier-Stokes Equations.
The Navier-Stokes equations are a coupled set of non-
linear partial differential equations for five unknowns: r, u,v, w, E.
Additional thermodynamic relations (equation of state,
etc.) are needed to relate pressure and temperature to
other thermodynamic variables.
Transport properties (m and k) must also be specified.
May also be functions of pressure and temperature
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Note:
The N-S equations (inviscid flow) have been simplified tremendously; however, still cannot be
solved due to the nonlinear terms (i.e., uu/x, vu/y, wu/z, etc.).
Numerical methods such as the finite element and finite difference methods are often used to
approximate the fluid flow problems.
The Navier-Stokes EquationFor frictionless or inviscid flows ( 0, 0 & xx= yy =
zz = - p), the momentum equation reduces to Eulersequation:
35
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Summing all terms of heat added and dividing by dxdydz gives
the net rate of heat transfer to the fluid particle per unit volume:
Fouriers law of heat conduction relates the heat flux to the local
temperature gradient:
The total rate of work done by surface stresses can be
calculated, however for brevity we only consider x-components
of stresses.
Rate of work done (x-direction), normal =
Rate of work done (x+ x), normal =
38
Energy Equation
qdivz
q
y
q
x
q zyx
z
Tkq
y
Tkq
x
Tkq zyx
zyu xx .
zyxx
uu xxxx
..
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Total of work done (x-direction), tangential =
Note that equation for stresses is similar to momentum term,
taking similar form:
Where vicious terms can be given as dissipation function , any
body forces by S & heat flux can be replaced by temperature
gradients, hence
39
Energy Equation
z
w
y
v
x
u zxyxxy ...
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This far E has not been defined, but this E could be
defined as Internal energy, kinetic energy etc. Note SE is
source term.Example: For 2D incompressible flow, neglecting KE so h
can be reduced to CpT, also for most fluid engineering
problems local time derivative of p and dissipation function
is neglected, hence equation derived becomes:
Local accelerationAdvection Diffusion
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Energy Equation
Equation of State
),( TP
TCC
Tkk
T
pp
)(Property Relations
This far E has not been defined, but this E could bedefined as Internal energy, kinetic energy and gravitational
energy (body forces & includes effect of potential energy)
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Summary of Equations
The system of equations is now closed, with seven equations
for seven variables: pressure, three velocity components (u,v,
w), enthalpy, temperature, and density.
Under
Source term
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A Generic Form of Basic Equations
Note significant commonalitiesbetween the various equations.
Turbulence equations
(Not derived ) see it
takes same form.
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A Generic Form of Basic Equations
If Energy: specific heat generation
0
zyx
u wv1If mass:
If Vmomentum:V
u x
pS
1
T
k
qST
Using a general variable , the conservative form of all fluid
flow equations can usefully be written in the following form:
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Exact Solutions of the NSE
Solutions can also beclassified by type or
geometry
1. Couette shear flows
2. Steady duct/pipe flows
3. Flows with moving
boundaries
4. Similarity solutions
5. Asymptotic suction flows
6. Wind-driven Ekman flows
There are about 80
known exact solutions
to the NSE
The can be classified
as:
Linear solutions where
the convective
term is zero
Nonlinear solutionswhere convective term
is not zero
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Exact Solutions of the NSE
1. Set up the problem and geometry, identifying allrelevant dimensions and parameters
2. List all appropriate assumptions,
approximations, simplifications, and boundaryconditions
3. Simplify the differential equations as much aspossible
4. Integrate the equations5. Apply BC to solve for constants of integration
6. Verify results
Procedure for solving continuity and NSE
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Boundary ConditionsIn order to solve the Navier-Stokes equations, we must supply
appropriate boundary conditions/initial conditions for thefluid domain.
Boundary conditions at walls (solid surfaces)
fluid sticks to the walls (no-slip condition)
thermal boundary conditions at wallsconstant temperature
constant heat flux
others (convection, radiation, etc.)
Inflow/Outflow boundary conditions Where fluid enters the domain, appropriate inflow
conditions must be specified
velocity components total pressure and flow directionscalar variables e.g. temperature
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Boundary Conditions
Where fluid exits the domain, assumptions must bemade about flow conditions at the outlet
static pressure is knownflow is fully-developed
Other boundary conditions
SymmetryPeriodicFar-field
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Example exact solution
Fully Developed Couette Flow
For the given geometry and BCs, calculate the velocityand pressure fields, and estimate the shear force per
unit area acting on the bottom plate
Step 1: Geometry, dimensions, and properties
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Example exact solution
Fully Developed Couette Flow
Step 2: Assumptions and BCs
Assumptions
1. Plates are infinite in x and z
2. Flow is steady, /t = 0
3. Parallel flow, Vy=04. Incompressible, Newtonian, laminar, constant properties
5. No pressure gradient
6. 2D, W=0, /z = 0
7. Gravity acts in the -z direction,
Boundary conditions1. Bottom plate (y=0) : u=0, v=0, w=0
2. Top plate (y=h) : u=V, v=0, w=0
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Example exact solution
Fully Developed Couette Flow
Step 3: Simplify3 6
Note: these numbers referto the assumptions on the
previous slide
This means the flow is fully developedor not changing in the direction of flow
Continuity
X-momentum
2 Cont. 3 6 5 7 Cont. 6
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Example exact solution
Fully Developed Couette Flow
Step 4: Integrate
Z-momentum
X-momentumintegrate integrate
integrate
55
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Example exact solution
Fully Developed Couette Flow
Step 5: Apply BCs
y=0, u=0=C1(0) + C2 C2 = 0
y=h, u=V=C1h C1 = V/h
This gives
For pressure, no explicit BC, therefore C3 can remain
an arbitrary constant (recall only P appears in NSE).
Let p = p0 at z = 0 (C3 renamed p0)
1. Hydrostatic pressure
2. Pressure acts independently of flow
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Boundary conditions
Finally, calculate shear force on bottom plate
Shear force per unit area acting on the wall
Note that w is equal and opposite to the
shear stress acting on the fluid yx(Newtons third law).
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Steady 2D incompressible, laminar f low between two
stationary parallel infinite plates with height = H
Example
Assumpt ions:Assumpt ions:
AIRAIR (Working fluid), Laminar(Working flu id), Laminar
L = 1.0 mL = 1.0 m H = 0.1 mH = 0.1 m
U = 0.01 m/sU = 0.01 m/s = 1.2 kg/m= 1.2 kg/m33 airair
= 2 x 10= 2 x 10--5 kg/m5 kg/m--ss
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Steady 2D incompressible, laminar flow between
two stationary parallel plates with H= 0.1 m and
L=0.5m
(a) Velocity vector plot(a) Velocity vector plot
CFD simulationCFD simulation
resultsresults -- the flowthe flow
field along channelfield along channel
length changes fromlength changes from
uniform at inletuniform at inlet
surface to parabolicsurface to parabolic
profi le as i t travelsprofi le as i t travels
downstream.downstream.
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Results CFD
(b) U velocity contour plot(b) U velocity contour plot
(c) V velocity contour plot(c) V velocity contour plot
In hydrodynamic entranceIn hydrodynamic entrance
region (x
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Results CFD
(d) Static Temperature contour plot(d) Static Temperature contour plot
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Physical Interpretation Continuity Eqn.
Continuity equation applied to infinitesimal small control volume for
2D case of the fluid flow between two parallel stationary plates.
Consider , then u(x+ x) > u(x), since more fluid is
physically leaving the CV then entering along the x direction, there
should be more fluid entering than leaving y direction. Here
and the v (y+y) < v(y)
0x
u
0y
v
Next. , then u(x+ x) < u(x), since more fluid is
physically entering the CV then entering along the x direction,
there should be more fluid leaving than entering y direction. Here
and the v (y+ y) > v(y). (CONTINUTIY EQ.
SATISFIED)
0x
u
0y
v
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Turbulence and its modelling
All flows become unstable above a certain Reynolds
number.
At low Reynolds numbers flows are laminar.
For high Reynolds numbers flows are turbulent.
The transition occurs anywhere between 2000 and 1E6,depending on the flow.
For laminar flow problems, flows can be solved using the
conservation equations developed previously.
For turbulent flows, the computational effort involved insolving those for all time and length scales is prohibitive.
An engineering approach to calculate time-averaged flow
fields for turbulent flows will be developed.
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Turbulence and its modelling
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Examples of simple turbulent flows
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Turbulence and its modelling
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Turbulence and its modelling
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Turbulence and its modelling
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Turbulence and its modelling
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Turbulence and its modelling
As air flows over and around objects in its
path, spiraling eddies, known as Von
Karman vortices, may form.
The vortices in this image were created
when prevailing winds sweeping east
across the northern Pacific Ocean
encountered Alaska's Aleutian Islands
Weddell sea in southern Atlantic
area near Antarctica,.
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Flow transitions around a cylinder
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Turbulence
. occurs at high Re
. are chaotic
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Turbulence
. are disspative
. are diffusive
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Turbulence ..
. rotation and
vorticity
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What is turbulence?
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Energy Cascade The continual transfer of energy from larger eddy to smaller and
smaller eddy is termed as Energy cascade .
Larger eddies highly anisotropic (varying in all directions),inertial effect dominates viscous effect.
Smaller eddies isotropic, viscous effect dominates and smears
out the directional ity of flow.Sources
Pope, Stephen B. Turbulent Flows.
Cambridge University Press
2000.
Tennekes H., Lumley J.L. A First Course
in Turbulence. The
MIT Press 1972.
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Turbulence
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Turbulence modelling objective
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Example: flow around a cylinder at Re=1E4
The figures show:
An experimental
snapshot.
Streamlines for time
averaged flow field.
Note the difference
between the time
averaged and the
instantaneous flow field.
Effective viscosityused to predict time
averaged flow field.
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Turbulence and its modelling
Fortunately!
The Engineers are often interested in time average
properties of the flow (mean v, mean p, mean stress etc.)
Thus by adopting suitable time averaging operator details
concerning to the instantaneous fluctuations can be
discarded. To illustrate the above influences of turbulent fluctuations
on the mean flow, instantaneous continuity and Navier
Stokes equations for an incompressible flow with constant
viscosity is produced (time averaging governing
equations), this more popularly known as ReynoldsAverage Navier-Stokes (RANS) equations.
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Turbulence and its modelling
To investigate the effects of fluctuations, we replace the
flow variables:
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Turbulence and its modelling
Considering the x-direction, the time average x-direction
momentum equations terms becomes:
Considering the y & z direction , the time average momentumequations becomes:
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T b l d it d lli
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Turbulence and its modelling
These terms are extra stresses terms ( 9 in all, 3 normal
stresses and 6 tangential stresses) and are called
REYNOLD STRESSES
REYNOLD STRESSES
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REYNOLD STRESSES
T b l d it d lli
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Turbulence and its modelling
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T b l l d lli
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Turbulence closure modelling
Turbulence models
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Turbulence models
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Turbulence models
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Turbulence models
Note Turbulence models are developed that close the
system of mean flow equations (Table presented earlier). In most engineering application the only the effects of
turbulence of mean flow is sought hence and details of
turbulent fluctuations are not resolved.These models uses
the Reynolds
AverageEquations and
forms the basis of
turbulence
calculations in
many CFD codes
Requires Time dependent flow equations solved
for mean flow and largest eddies and effects of
smaller eddies are modelled95
Turbulence models
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Turbulence models
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Turbulence models
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Turbulence models
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Boussinesq hypothesis
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Boussinesq hypothesis
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Turbulent viscosity
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Turbulent viscosity
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Turbulent Diffusivity
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Turbulent Diffusivity
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Predicting the turbulent viscosity
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Predicting the turbulent viscosity
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Mixing length model
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Mixing length model
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Mixing length model
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Mixing length model
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Spalart-Allmaras one-equation model
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Spalart Allmaras one equation model
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The k- model
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The k model
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Mean flow kinetic energy K
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Mean flow kinetic energy K
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Turbulent kinetic energy k
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Turbulent kinetic energy k
Model equation for k
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Model equation for k
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Dissipation rate - analytical equation
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ss pat o ate a a yt ca equat o
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Model equation for
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q
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Calculating the Reynolds stresses from k &
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g y
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k- model discussion
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More two-equation models
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q
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Improvement: RNG k-
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p
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RNG k- equations
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q
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Improvement: realizable k-
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p
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Realizable k- equations
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Realizable k- C equations
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Realizable k- positivity of normal stresses
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k- model
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Algebraic stress model
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Non-linear models
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Reynolds Stress Model
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Reynolds stress transport equation
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RSM equations
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RSM equations continued
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Setting boundary conditions
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Recommendation
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