Boundary Layer Finalppt
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Transcript of Boundary Layer Finalppt
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Boundary Layer Theory
Presented by:
Sadashiv Jha
A-61
B.Tech(Mechanical)
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Contents
Boundary Layers
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Boundary LayersAs a fluid flows over a body, the no-slip condition ensures
that the fluid next to the boundary is subject to large shear. A
pipe is enclosed, so the fluid is fully bounded, but in an open
flow at what distance away from the boundary can we begin
to ignore this shear?
There are three main definitions of boundary layer thickness:
1. 99% thickness2. Displacement thickness
3. Momentum thickness
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99% ThicknessU
U is the free-stream velocity
(x)
x
y
(x) is the boundary layer thickness when u(y) ==0.99U
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Displacement thickness
There is a reduction in the flow
rate due to the presence of the
boundary layer
This is equivalent to having atheoretical boundary layer with
zero flow
y
u
y
uU
U
d
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Displacement thicknessThe areas under each curve are defined as being equal:
0
dyuUq and Uq d
0
d dyU
u1
Equating these gives the equation for the displacement
thickness:
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Momentum thicknessIn the boundary layer, the fluid loses momentum, so
imagining an equivalent layer of lost momentum:
0 dyuUum andm
2
Um
0
m dyU
u1
U
u
Equating these gives the equation for the momentum
thickness:
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8
BOUNDARY LAYER ON A FLAT PLATE
Consider the following scenario.
1. Asteady potential flow has constant velocity U in the x direction.
2. An infinitely thin flat plate is placed into this flow so that the plate is
parallel to the potential flow (0 angle of incidence).
Viscosity should retard the flow, thus creating a boundary layer on either side
of the plate. Here only the boundary layer on one side of the plate is
considered. The flow is assumed to be laminar.
Boundary layer theory allows us to calculate the drag on the plate!
xy
U
U
u
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9A STEADY RECTILINEAR POTENTIAL FLOW HAS ZERO
PRESSURE GRADIENT EVERYWHERE
xy
U
U
u
plate
A steady, rectilinear potential flow in the x direction is described by the
relations
According to Bernoullis equation for potential flows, the dynamic pressure of
the potential flow ppd is related to the velocity field as
Between the above two equations, then, for this flow
0y
v,Ux
u,Ux
const)vu(21p 22pd
0y
p
x
p pdpd
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11NOMINAL BOUNDARY LAYER THICKNESS
xy
U
U
u
plate
Until now we have not given a precise definition for boundary layer thickness.
Here we use to denote nominal boundary thickness, which is defined to be
the value of y at which u = 0.99 U, i.e.
U99.0)y,x(uy
x
y
u
U
u = 0.99 U
The choice 0.99 is arbitrary; we could have chosen 0.98 or 0.995 or whatever
we find reasonable.
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12STREAMWISE VARIATION OF BOUNDARY LAYER
THICKNESS
Consider a plate of length L. Based on the estimate of Slide 11 of
BoundaryLayerApprox.ppt, we can estimate as
or thus
where C is a constant. By the same arguments, the nominal boundary thickness
up to any point x L on the plate should be given as
UL,)(~L
2/1ReRe
2/12/1
U
L
CorU
L
~
2/12/1
UxCor
Ux~
xy
U
U
u
plateL
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Laminar boundary layer growth
+ d
dy
x
y
Boundary layer => Inertia is of the same magnitude as Viscosity
a) Inertia Force: a particle entering the b.l. will be slowed from a velocity
U to near zero in time, t. giving force FIU/t. But u=x/t => t l/U
where U is the characteristic velocity and lthe characteristic length in the
x direction.
Hence FIU2/l
b) Viscous force: F/y 2u/y2U/2
since U is the characteristic velocity and the characteristic length in the
y direction
(x)
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Laminar boundary layer growth
Comparing these gives:
U
l
So the boundary layer grows according tol
Alternatively, dividing through by l, the non-dimensionalised
boundary layer growth is given by:
lRl
1
Note the new Reynolds number
characteristic velocity and
characteristic length
U
U llRl
)(U
5 Blasius
lU2/lU/2
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Boundary layer growth
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Length Reynolds Number
UlRl
l
U
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Flow at a pipe entry
l
U
d
If the b.l. meet while the flow is still laminar the flow in the pipe will be laminar
If the b.l. goes turbulent before they meet, then the flow in the pipe will beturbulent
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Boundary layer equations for laminarflowThese may be derived by solving the Navier-Stokes equations
in 2d.
0 yv
xu
dtdu
yu
xu
xp
1 2
2
2
2
Continuity MomentumU
Assume:
1. The b.l. is very thin compared to the length
2. Steady state
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Boundary layer equations for laminarflow
y
uv
x
uu
y
u
x
p
12
2
This gives Prandtls b.l. equation:
rate of change of u with
x is small compared to y
Blasius produced a perfect solution of these equations valid
for 0
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Blasius Solution
0
5
0 1
u/U
y'
y' f' (or u/U) f''
0 0 0.332
1 0.330 0.332
2 0.630 0.3233 0.846 0.267
4 0.956 0.161
5 0.992 0.064
6 0.999 0.002
7 1.000 0.000
l
Uy'y
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Laminar skin frictionThe shear stress at the surface can be found by evaluatingthe velocity gradient at the surface
00 y
u
The friction drag force along the surface is then found by
integrating over the length
dxy
ubF
0y0
f
l
where b is the breadth of the surface
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Laminar skin frictionFrom the Balsius solution, the gradient of the velocityprofile at y=0 yields the result:
0.5
x0 Rx
U
0.332
The shear force can be obtained by integration along the surface
0.5
0
0f R0.664UbdxbF l
l
The frictional drag coefficient can then be calculated
21
R33.1AU
FC
2
21
ff
l
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Force and momentum in fluid
mechanics - refresherNewtons laws still apply. Consider a stream
tube:
u1,A1
q1=u1A1
u2,A2
q2=u2A2
mass entering in time, t, is u1A1tmomentum entering in time, t, is m1 = (u1A1t)u1
momentum leaving in time, t, is m2 = (u2A2t)u2
Impulse = momentum change, F = (m2m1)/ t = (u22
A2-u12
A1)
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The von Karman Integral Equation(VKI)
A
B
C
D
Flow enters on AB and BC, and leaves on CD
1 2
2 -1
x
U
u1(y)u2(y)
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VKIThe momentum change between entering and leaving the control volume
is equal to the shear force on the surface:
122
0
2
1
0
2
20 Udyudyux12
(CD) (AB) (BC)
By conservation of fluid mass, any fluid entering the control volume must
also leave, therefore
12
0
1
0
212 )(
dyudyuU
12
0
1
2
1
0
2
2
20 dyUuudyUuux
Force onfluid
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VKI
0
2
0 dyUuuddx
As x 0, the two integrals on the right become closer and
the equation may be written as a differential:
0
2
0 dyU
u1
U
u
dx
dU
The integral is the definition of the momentum thickness, so
dx
dU m20
dx
dUUd if U(x)
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Turbulent boundary layers
The assumption is made that the flat plate approximates tothe behaviour in a pipe. The free stream velocity, U,
corresponds to the velocity at the centre, and the boundary
layer thickness, , corresponds to the radius, R.
1/7 Power Law
From experiments, one possibility for the shape of the
boundary layer profile is71
y
U
u
and measurements of the shear profile give
41
U
U0.0225 20
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Turbulent boundary layers
Putting the expression for the 1/7 power law into the
equations for displacement and momentum thickness
72
7
,8
md =99%
d
m
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Turbulent boundary layersdx
dU m20 becomes
dx
dU
72
7 20
Equating this to the experimental value of shear stress:
41
U
0.0225
d
d
72
7
x
Integrating gives:
5
1
Ux0.37x
The turbulent boundary grows as x4/5, faster than the
laminar boundary layer.
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Turbulent boundary layersMomentum thickness
51
Ux0.036x
72
7m
To find the total force, first find the shear stress
dx
dU m20
then integrate over the plate length
m
2
0
m2
0
0 Udx
dx
dUdxF
ll
f
For a plate of length, l, and width b,
51
UbU0.036F 2
l
lf51
0.074RC lf )10R10*5(
75 l
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Logarithmic boundary layerFrom the mixing length hypothesis it can be shown that
the profile is logarithmic, but the experimental values
are different from those in a pipe
yVln85.556.5
V
u *
*
and the friction coefficient llf R
A
Rlog
455.0
C 58.2
(A is a correction constant if part of the b.l. is laminar)
)10R0( 9 l ritrit
58.2
rit
RR
1.328
Rlog
455.0c
cc
A
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Quadratic approximation to the
laminar boundary layer
2
y
y2U
u
Remember - boundary layer theory is only applicable inside
the boundary layer.
This is sometimes written with =y/ and F()=u/U as
2
2F It provides a good approximation to the shape of the
laminar boundary layer and to the shear stress at the surface
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Turbulent Boundary Layer
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Laminar Sub-Layer
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