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h pter 6
Recapitulation
6 Summary
Figure 6.1 schematizes the results we have reached thus far in our first five chapters.
Note the dividing line in Fig. 6.1. In Chap. 1 we stated that any problem has two
fundamental aspects to its solution: 1) we must select the correct mathematical tool
to describe the functions and their changes, and b) we must incorporate the appropriate
physical laws that define the problem fully.
Three methods govern the mathematical modeling of any problem: methods of
analysis, description, and approach. When we
n lyze
a problem, we must first select
the appropriate control: we can choose either a system where we identify a fixed
mass), or a control volume where we identify a volume of space). Once we have
selected the control, we then determine the method that describes the fluid s behavior
for that control. we have chosen a system, we select the Lagrangian description,
because we want to study the history of a fixed mass.
we have chosen a control
volume, we select the Eulerian description, because mass can enter, leave, accumulate,
or deplete with respect to the control. Finally, we must decide how to
ppro ch the
description of the control. Two forms of approach are available: the integral form
I.F), or the differential form D.F.). The former is used for large volumes or quantities
of mass, the latter for differential or elemental sizes.
Referring again to Fig. 6.1, we note that whatever choices we have made within
the three methods of modeling, we will eventually have to consider the I.F.) general
property balance Eq. 4.13), or the D.F.) general property balance Eq. 4.16). In
Chap. I we applied the conservation principles of physics to these equations. Applying
the conservation of mass, we derived a mass balance equation that predicts the behavior
of a parcel of mass or mass through a continuous volume of space. Applying the
conservation of linear and angular momentum, we produced a similar result for the
behavior of the fluid flow linear and angular momentum. Applying the conservation
of energy, we found an energy balance for either an elemental volume or a macroscopic
one. The results of applying conservation laws to fluid flow are summarized as follows.
l
The D.F.) equation for the conservation of mass is
ap
V pV
o
6.1)
4
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Properties of fluids
onservation law:
onservation of
momentum
Mathematical
modeling
igur
6
chematic introduction to the theory fluid mechanics
Physics
f fluids
avicr Stokes
Eg.6.4
I
om ntum
I
Eg
6.5-68
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6.1 Summary /
2. The I.F. equation for the conservation of mass is
i
pdV
+
at
t pV dA = 0
6.2
The one-dimensional incompressible form is
Q = VA
3. The D.F. equation for the conservation of linear momentum is
6.3
av
I I
- +
V·V)V = - -
Vp +
g
+ VV2V + -
vV V·V) 6.4
p 3
For incompressible flow, V V = 0, and the last term vanishes.
4. The I.F. equation for the conservation of linear momentum is
i pV dV + f pV V ·dA = I-F
arJv
A
For incompressible steady one-dimensional flow, the equation reduces to
I- F = pQ.lV
5. The I.F. equation for the conservation of angular momentum is
i
pr X V dA +
f
pr x V V dA)
=
I-r x F
arJv
A
For incompressible steady one-dimensional flow, the equation reduces to
6. The D.F. equation for the conservation of energy is
aw
a
- = - pe
+ V [ e + p/p pV
dt mech at
. .
kV + 2J.l.V·S] - 2J.l. S·V ,V
6.5
6.6
6.7
6.8
6.9
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/ Chapter 6 Recapitulation
7. The I.F. equation for the conservation of energy is
. . a
_ V
2
v
2
iQe + iWe =
Jv p
i
+ 2 + gz dV +
J
P i + 2 + gz V .
A
6.10
For incompressible, steady, one-dimensional flow, Eq. 6.10 can be expressed as
p
y p y
CWe mech
+ - + + z . - - + + z = h
f
g I g
e
6.11
The foregoing set of equations represents the governing equations of motion for
fluid flow. We shall next summarize some special forms of the governing equations.
6 Special Forms the Governing Equations
Special forms of some of the governing equations of motion are of value when we
deal with certain types of fluid flow. For example, whenever the flow is
1. Steady:
2. Inviscid:
3. Two-dimensional:
a
t
v
a
az
= 0
= 0
= 0
6.12
6.13
6.14
where
x
and y are the principle direction of flow.
4. One-dimensional:
a
a
= -
az
=
0
6.15
where
x
is the principle direction of flow.
5. Incompressible:
= 0
6.16
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6
SpecU
Forms
the Governing Equations / 5
6. Irrotational:
7. Definition of a real average:
x
L
°
dA
6.17)
6.18)
Substitution of these results in any of the governing equations helps reduce the
complexity of the equations. Special forms of the equations can now be constructed.
Certain D.F.) equations of linear momentum are presented in Table 6.1. So important
are these forms in fluid dynamics that we will devote entire chapters to them. For
example, Laplace s equation is the governing equation for potential theory the topic
of Chap. 12). The differential equation for the accelerating flat plate is important as
it introduces us to the concept of the boundary layer the topic of Chap. 14). Poiseuille s
equation is important in describing laminar flow in a pipe the subject of Chap. 10).
A solution of Euler s equation yields one of the most widely used equations in fluid
dynamics, namely, Bernoulli s equation.
All the equations shown in Table 6.1 have exact solutions. Though the list is far
from complete, it does illustrate that, for certain fluid flows, the Navier-Stokes equa
tions call be reduced to a form where we can obtain closed form analytic solutions.
This will be pursued in Chap. 9.
Figure 6.2 shows how we might take one of the two forms of approach the D.F.)
and apply it to a general class of incompressible fluid flows. We start by identifying
the two governing equations: the continuity equation and the Navier-Stokes equation.
The types of flows we can treat depend upon the relative significance of the
various acceleration terms in the Navier-Stokes equation. Referring to Fig. 6.2, we
can identify the following terms:
I.
@
The local acceleration, which is important only if the fluid properties change
at a point in the flow field.
2. ® The convective acceleration, which would be zero if the flow is uniform
because there is no change in the velocities in space.
3.
@
The pressure acceleration, which would vanish because, for a fluid with a
free-surface, the pressure cannot change except hydrostatically).
4.
@
The body force per unit mass. This deceleration would vanish for two
dimensional planar flow.
5.
0
The viscous deceleration, which vanishes for an inviscid fluid.
All incompressible flows using the D.F.) in describing the fluid motion must
satisfy this Navier-Stokes equation. We have already studied some special cases:
• Hydrostatics:
@ = ® = =
0, in Chap. 3.
• Inviscid flows: 0 0, in Chaps. 4 and 5.
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ble 6.1
Equations
of
Fluid Flow That Have Exact Solutions
Assumptions
Origin
Equation
Mathematical Expression
Coord. System
Name
References
equation
v =
0
p = constant
a
=
0
a
z
o
4.109)
i)
ii)
iii)
iv)
v
av av
la p
- + v
=
-
at as p as
au au au
- + +
v
at ax ay
aV av av
- +
+
v
at ax ay
aV
r
aV
r
V -
at r ar r
e e r e
at + vra +
p
}
x
ap
y
ar
Intrinsic
Rectangular
Polar
Euler s equation
4.110
p = constant
Vxv o
Potential flow)
p = const.
~
at
g
=
0
V = w = 0
4.24
4.109)
vi)
vii)
viii)
a
2
j a
2
j a
2
j
=0
ax
a
y
az
a
2
j I a j I
a
2
j
j>
=0
ar
r r
2
az
d
u
_
dp
dy
-
l dx
Rectangular
Cylindrical
Rectangular
Laplace s equation
Poiseuille s equation
12.2
9.6
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Table 6
Con t.)
Origin
References
Assumptions
Equation Mathematical Expression Coord. System
Name equation
p = canst.
~
4.109) ix)
v
2
_
dp
Axisymmetric
-
at
p dr
g = 0
u, = w - 0
x)
d v + = 0
Polar
Inviscid circular
dr
2
dr r
vortex flow
v = 0
p = canst.
~
4.109) xi)
d
2w
dw dp
Cylindrical
Hagen-Poiseuille
=
Prob.4.69
at
dr? r dr
I l
dz
equation
g = 0
a
- = 0
az
u, = = 0
p = canst.
a
4.109) xii)
v dv, = dp + v a
2v,
+ . .av,
=
at
dr p dr ar
2
r dr
Cylindrical Hamel s equation
= 0
a
2v,
v,
az
+ ?
2
- ?
g = 0
oI l
ap
2 l
Bu,
= w = 0
xiii)
r
2
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ble 6.1 Con t.)
Assumptions
p
=
canst.
g = 0
p =
canst.
v = w = 0
p = canst.
g
= 0
Va = w = 0
Axisymmetric
Origin
Equation
4.109
4.109
xiv
xv
Mathematical Expression
au a
u
at ay
Bu
r
1
ap
- + V - =
at r ar p ar
v v
r
+
r
_
r
ar
2
r ar r
2
Coord. System
Rectangular
Polar
Name
Accelerating
flat plate
Bubble dynamics
References
equation
9.24
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From Fig.-6.1
D .F . of
Navier-Stokes equation
continuity equation
av
I
V
•
V)V
V
P
- g -
I
V
= 0
V
·v=o
at
p
0
0 0
0
0
=0
L T I
t
0=0
0=0=0
0=0=0
0=0
0=0=0=0
w=o
u
u
v w
=0
Euler s equation
Hydrostatics
« a/
Potential flow
Prandtl boundary
layer equation
0=0
Couette flow
[ 0 0 0 ]
d streamline)
Blasius solution
Poiseuille flow
V
2
c
= 0
Equation of a
Etc.
Bernoulli s equation
streamline
Boundary layer thickness Kutta-Zhukouski
Drag on flat plate
Etc.
law
From
Fig. 6.1
Figure 6.2 Continuation of schematic of introduction to the theory of fluid mechanics
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350
/
Chapter 6 Recapitulation
In the chapter to follow, we shall study
• Poiseuille flows: @ 0, in Chaps. 9 and 10.
• Potential flows: @
0
0, in Chaps. 12 and 13.
• Boundary layer flows:
@
0,
in Chap.
14.
In particular, we shall examine a variety of applications. For example, we shall
study the principle of flight Kutta-Zhukouski law) which arises out of potential flow
theory, or the friction drag on a ship s hull, which arises out of the Blasius solution
of the boundary layer flow theory. We shall learn about pipe flow and free channel
flow. Not all branches of fluid dynamics can be treated in this text, but many shall
be.
6 3 Problem Solving Technique
How do we solve fluid dynamics problems? There is no mutually agreed upon single
way to set up solutions. The choice of problem-solving technique may depend on
nothing more than the familiarity and confidence of the user. For ease and clarity,
especially for beginners, we suggest the following problem-solving methodology:
Step
Identify the characteristics of the fluid and flow field.
1. List the data given and the results required.
2. Check to see if the fluid is
a) incompressible or compressible
b) inviscid or real
c) steady or unsteady
d) one-, two-, or three-dimensional flow
e) rotational or irrotational
Step 2
Select the method of approach.
1. Examine the problem to see if quantities are to be solved at a point in the flow
D .F. ), or at some boundary, or on some volume of a large control
I.F.).
2. Draw and label any necessary diagrams needed for the solution. Examine what
forces or stresses are acting on the control and what transfer of energies through
the control may exist.
3. Determine if the description takes place with respect to a
fix
reference frame
or a moving reference frame. The former utilizes absolute velocities and accel
erations; the latter utilizes relative velocities and accelerations.
a) Select the appropriate coordinate system that best describes the motion.
b) Let one the coordinates be oriented in the direction of the flow.
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6 3 Problem Solving Technique
/
35
Step 3
Write the appropriate form of the governing equations of flow see the summary of
equations in Sec. 6.1 .
1. Apply the results of Step 1 to reduce the equations to their simplest
form,
2. Examine all conditions given at a point or boundary.
a Identify all kinematic conditions.
b Identify all stress conditions.
c Identify all inn r conditions.
d Identify all initial conditions.
Step 4
Solve the problem.
1. Think about the problem in terms of its physical significance. Each term of the
reduced governing equation and its boundary conditions have a physical inter
pretation. The dimensions of each term must be identical and correct.
2. Check to see if there are sufficient equations to solve for the unknowns. not,
then additional equations will have to be sought, e.g., the equation of state and
stress-strain relationships.
3. Select a method for solving the reduced governing equations. The following two
sections offer a few aids in selecting an appropriate method.
6 xamples ofProblem Solving Technique
We are now at a position to apply our problem-solving technique to a flow problem.
We have all the necessary tools to commence building a solution: the governing
equations of fluid flow; the various methods of analysis, description, and approach to
treat a problem; ways to fit the equations to the given problem and simplify their
expressions; the mathematical symbols and operators necessary to describe the behavior
of the flow and the methods to solve them; and the step-by-step procedure to bring
all this together. Two problems will be analyzed in detail. The first will involve the
D.F. approach, and the second will involve the LF. approach.
Example 6 The D.F. Approach
Consider a steady two-dimensional incompressible viscous flow with no body
forces, where the pressure gradient ap/ax is zero and the y-component of velocity
v
is equal in magnitude to the kinematic viscosity
v
and is a constant. At the
location y equals zero, the shear stress y is unity. a Find an expression for
the shear stress y and vorticity component about the z-axis that is valid
everywhere in the flow field. b Find the distribution of velocity given
u
equals
zero at y equals zero.
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352
hapter
6
ecapitulation
Example 6 1
Can t.)
Solution:
Step 1.
Identify the characteristics of the fluid and flow field:
• The flow is steady:
o
at
• The flow is two-dimensional:
o
• The flow is incompressible:
p const.
• The flow is real:
v¥-O
• There are no body forces:
g 0
• The pressure gradient is zero:
ap
ax
o
• The velocity component v is given:
v
v
dynamic viscosity
• A boundary condition is given:
xy y o
• Find xy x, z,
t
and
x, z,
t
Step 2.
Select the method of approach:
•
D.F.
• No external forces, no energy transfers
• Fixed reference frame Cartesian
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6.4 Examples ofProblem-Solving Technique / 353
Example 6 Con t.)
y
........ u x y z t
pxy= 1.0, u = 0
Figure E6.1
Step 3.
Write the appropriate form of the governing equations of flow:
• Continuity equation:
J 0
au
+
?1. =
0
ax
/y
I
• Navier-Stokes equations:
au au
~ j
a
u
a
u
+
v
v
ax ay p x
ax
2
ay
o
0 0 0
+
vj
=
1 ap
J
+
V
2
+
2
pay
since we were given
ap ax
= 0 and v = v.
Equation i becomes
au
= 0
ax
i
ii
iii
iv
which means that since the velocity component u is not a function of x Z and
t it is at most a function only of y.
In a similar fashion, from Eq. iii ,
ap
=
0
Thus, the pressure everywhere in the flow field is constant.
v
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354 hapter 6 ecapitulation
Example 6 1
Con t.)
The Navier-Stokes equation, Eq. ii , reveals that
vi
Step
Solve the problem.
We can solve this problem analytically. Integrating Eq. vi once yields
vii
where
is an arbitrary constant of integration. To evaluate it, we use the
boundary condition that
du I
xy = l dy
y
=
From Eqs. vii and viii , we obtain
I
l
a The shear stress distribution is from Eqs. vii and ix ,
The vorticity component is now easily obtained as
viii
ix
x
or
=
=
du
dy
xi
xii
The quantities
xy
and are shown plotted in Fig. 6.3 for values of negative
y
b If we impose the condition that the velocity
u
is zero at
y
equals zero,
we obtain
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6.4 Examples of Problem-Solving Technique
/ 355
Example 6 1
Con t.]
Velocity profile
6.0
.0
.0
.0
{
Shear stress profile
Vorticity profile
2.0
.0
.
/
/
I
I
I
I
I
I
I
O L . _ _ L
L J
L _ J
o
1.0
0.8
pxy
0.6
1L z
0.4
-ILU
0.2
y
Figure 6.3 Example of the D.F. problem.
xiii
1
u
=
e
Y
- 1
fl.
as the velocity profile. The distribution is shown plotted in Fig. 6.3 above.
This completes the solution.
Example
6.2.
The
LF.
Approach
Water enters a 60° horizontal reducing elbow with a velocity of 15 ftls at a
pressure of 12 psi. Calculate the x and y-components of the reaction force acting
on the elbow. The entering diameter is 12 in., and the exit diameter is 8 in.
Neglect viscous effects.
Solution:
Step 1.
Identify the characteristics of the fluid and flow field:
• The flow is steady:
o
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6
I Chapter
6
Recapitulation
Example 6 Con r.)
• The flow is one-dimensional:
• The flow is incompressible:
p const.
• The flow is ideal:
v = 0
• There are no body forces:
W
• Given data:
15 ft/s
Pi
12 psi
D 12 in.
De 8 in.
e
°
Step :
Select the method of approach:
•
I.F.
• External forces are pressure forces; no energy transfers
• Fixed reference frame Cartesian
t
12in
p = 12 psi
;
f s iii
8 n
Figure E6
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6.4 Examples
of
Problem-Solving Technique I 7
x mple 6.2
Con t.)
Step 3.
Write the appropriate form of the governing equations of flow:
• Continuity equation:
-
-
Q = VA ; = VA e
• Linear momentum:
• Energy:
p
V2
p
V
2
z
=
z
Y 2g i Y 2g
e
Step 4.
Solve the problem:
From continuity equation i ,
11 11
15 X - X 12
2
= V
X - X 8
2
4
2
4
or
- 9
V
2
= -
X 15
=
33.75 fps
4
From Bernoulli equation iv ,
PI
P2
V
= -
Y 2g Y 2g
P2
PI V
=
Y Y 2g 2g
or
P2 12 X 144
_ _ 52
_ 33.752
Y 62.4 64.4
P2
=
5.85 psi
From the momentum equation ii ,
z F
x
=
R P l P2A2 cos 60°
- -
=
pQ V2 cos e - VI )
pQV
2
=
1.94
X
11.8
X
33.75
=
773
i
ii
iii
iv
v
vi
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8 /
Chapter 6 Recapitulation
Example 6.2
Con t.)
pQV
= 1.94 x 11.8 x 15 = 343
P A
=
5 . 8 5 ~ 8 2
=
294
p,A,
=
12
~
12
2
=
1357
Therefore
R =
-773 .5
343 - 294 .5 1357
or
R = 11671bf
From the momentum Eq. iii ,
I F
= R; P A sin 60° = p V
sin 60° - 0
therefore,
R; = 294 .866 773 .866 = 254.5
670
or
s = 924.5 Ibf
This completes the solution.
vii
viii