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Southern Methodist University
Bobby B. Lyle School of Engineering
CEE 2342/ME 2342 Fluid Mechanics
Roger O. Dickey, Ph.D., P.E.
III. BASIC EQS. OF HYDRODYNAMICS
C. Integral Forms of the Basic Equations
3. Linear Momentum
Reading Assignments:
Chapter 5 Finite Control Volume Analysis;
Sections 5.2.1 Derivation of the Linear
Momentum Equation
Section 5.2.2 Application of the Linear
Momentum Equation
C. Integral Forms of the Basic Equations
Linear Momentum
When Isaac Newton originally formulated his
laws of motion, instead of expressing his second
law as F=ma he stated it in terms of the rate of
change of momentum; where momentum is
defined as mass times velocity, mV.
For a system of mass m, Newton stated his second law as:
Expressing this narrative equation mathematically:
FVDtmD
system theon actingforces external theof Sum
systema of momentumlinear theof change of rate Time
For a third time, reconsider Reynolds Transport
Theorem (RTT) for physical property B, where
b is the amount of the physical property per unit
mass of fluid :
CSCV
dAbVdbtDt
DB nV ˆ
Flux of B, i.e., transport rate of B per unit area
Amount of B per unit volume
For the linear momentum equation, i.e., principle
of conservation of linear momentum, B = mV,
and b = mV/m = V. Substituting into the RTT
expression:
CSCV
dAVdtDt
mD nVVVV ˆ
Substituting from Newton’s
Second Law and rearranging:
[Equation 5.22, p. 213]
Integral Form of Linear Momentum Equation
DtmD VF for
FnVVV
CSCV
dAVdt
ˆ
Expressing each term in words for clarity:
For steady flow : 0t
FnVVCS
dAˆ
Time rate of change of the linear momentum of the CV contents
FnVVV
CSCV
dAVdt
ˆ
Net rate of flow of linear momentum
across the CS
Sum of the forces acting on the contents of the CV
Integral Form of Steady Linear Momentum Equation
*Important Points –
(i) can be viewed in exactly the same
manner as the forces on a free-body. In this
case, the mass m inside the CV at time t is the
free-body under consideration, and the CS
delineates the free-body boundary.
F
(ii) Forces involved are usually placed into two categories;
• Body forces act on the entire contents of the CV, e.g., gravitational forces or weight
• Surface forces acting on or along the CS, e.g., fluid pressure forces, reaction forces from solid boundaries or immersed objects including both normal (pressure) and tangential (shear stress) forces
(iii) The linear momentum equation is a vector equation involving V on the left-hand side, and on the right; is a scalar. Thus, it may be written as three component, scalar equations. For steady flow and ;
F nV ˆ
xCS
FdAu nV ˆ
yCS
FdAv nV ˆ
zCS
FdAw nV ˆ
kjiV ˆˆˆ wvu
(iv) Very careful consideration must be given to algebraic signs for the forces, velocities, and the vector dot product in order to obtain correct results.
• is (+) for outflow from the CV, and () for inflow into the CV
• u, v, w, Fx , Fy , and Fz are (+) when
directed along the (+) x-, y-, and z-axes respectively, and negative when oppositely directed.
nV ˆ
nV ˆ
If the CV is fixed in space, it is of finite size, there are a finite number of inflow and outflow streams, and uniform flow prevails in the various inflow and outflow regions of the CS, then piecewise integration of the steady flow linear momentum equation over all inflow and all outflow regions of the CS yields finite summations. For example, along the x-axis:
All
xAll All
ininoutout mumu F
(+) because outflow regions have
0ˆ nV
() because inflow regions have
0ˆ nV
Consider a differential area element dA on the inflow region of a CS enclosing a fluid system, having pdA as the magnitude of the pressure force:
nF ˆpdApressure dA
V
n̂
In this scenario, velocity V is directed inward
while the unit normal vector, , is directed
outward yielding a negative dot product,
0cos 27090 because 0ˆ nV
n̂
Similarly, for a differential area element dA on the outflow region of a CS enclosing a fluid system, having pdA as the magnitude of the pressure force:
nF
ˆ pdApressure
dA
V
n̂
In this scenario, velocity V is directed
outward, likewise the unit normal vector, , is
directed outward yielding a positive dot
product,
0cos 9090 because 0ˆ nV
n̂
Applying similar conditions and reasoning along all
three coordinate axes, and substituting inQin for
and outQout for yields:
All
xAll All
inininoutoutout FQuQu
All
yAll All
inininoutoutout FQvQv
All
zAll All
inininoutoutout FQwQw
inm
outm
In most common engineering applications, the
various inflow and outflow streams have the same
constant density, , and the previous vector
component equations are slightly simplified to:
All
xAll All
ininoutout FQuQu
All
yAll All
ininoutout FQvQv
All
zAll All
ininoutout FQwQw
Refer to Handouts — III.C.3. Linear
Momentum Equation Examples for practical
examples dealing with application of the linear
momentum equation.
*Hydrodynamics Problem Solving Hints –
(1) Clues about when to apply the three Basic Equations of Hydrodynamics for problem solving:
• Continuity – virtually always
• Energy – when elevations, pressures, velocities, energy losses, energy input, or energy output are required
• Momentum – when forces are required
(2) The Continuity Equation is always
applicable, regardless of the presence or
absence of mechanical devices adding energy
to, or removing energy from the CV.
(3) For uniform flow, streamlines are straight
and parallel and the pressure distribution is
hydrostatic perpendicular to the direction of
flow. Stated another way,
(i.e., piezometric head is constant), along any
line or planar cross-section perpendicular to
the direction of flow.
Constant
pz
(4) Although all points on a plane perpendicular to
the flow have the same value of , it is
customary in uniform pipe flow to use the
elevation, z, and pressure, p, at the pipe
centerline as representative of a given cross-
section. Furthermore, it is often assumed that
pressure gauge readings give the pressure at the
pipe centerline (often a good approximation):
pz
p
Elevation Datum, z = 0
z
p = (z) 0z
z
Pressure GaugePipe Cross-section
(5) Although all points on a plane perpendicular to the direction of flow have the same value of , it is customary in uniform open
channel flow to use the elevation, zb , and
pressure, pb=γhb, at the channel bottom as
representative of a given cross-section. Further, it is often assumed that the angle, , that the sloping channel bottom makes with the horizontal is small, yielding cos 1.0 (often a good approximation for both natural and human-constructed channels):
pz
Elevation Datum, z = 0
zb
Free Surface, y = yfs
Channel Bottom, y = 0
pb = h
bpb = (y
fs cos)p
b yfs
y
x
z
hb
h
Open Channel Longitudinal-section
≈ 1
x-, y-coordinate axes parallel and normal to channel bottom
Substituting γyfs for pb , the Energy Equation for
open channel flow becomes,
Dividing out γ in the pressure head terms,
Lfs
bfs
b hg
Vγy
zg
Vγy
z 2
2
222
2
211
1
Lfsbfsb hg
Vyzg
Vyz 22
22
22
21
11
Finally, notice that for all points on a planar cross-
section perpendicular to the flow,
Therefore, drop the subscripts on zb and yfs
yielding the customary form of the Energy
Equation applied in open channel flow:
Lhg
Vyzg
Vyz 22
22
22
21
11
fsfsb yzyzyz z0Constant
(6) When applying the Linear Momentum Equation, the forces generated by momentum transfer may be visualized in two ways: (i) impact of inflow streams “crashing” into the fluid already inside the CV, and (ii) recoil from outflow streams “shooting” from the CV. This reveals that the pressure force component and the momentum transfer component in a given coordinate
direction at a given cross-section (e.g., Fpx1 and
u1Q1) are always additive.
That is, after solving the Linear Momentum Equation for resultant reaction force components,
either FRx or FRy, and substituting appropriate
numerical values for pressure force and velocity vector components, algebraic signs may be quickly checked for accuracy because each pair of pressure force and momentum transfer
components along the same coordinate axis—Fpx1
and u1Q1, Fpy1 and v1Q1, Fpx2 and u2Q2, Fpy2
and v2Q2—should have the same algebraic sign.