fluid_mechanics
440 Chapter 8 ■ Viscous Flow in Pipes or 322 V 2 1 0.4V 2 3 (2) where V 1 and V 3 are in fts. Similarly the energy equation for fluid flowing from B and C is or For the given conditions this can be written as Equations 1, 2, and 3 1in terms of the three unknowns V 1 , V 2 , and V 3 2 are the governing equations for this flow, provided the fluid flows from reservoir B. It turns out, however, that there is no solution for these equations with positive, real values of the velocities. Although these equations do not appear to be complicated, there is no simple way to solve them directly. Thus, a trial-and-error solution is suggested. This can be accomplished as follows. Assume a value of V 1 7 0, calculate V 3 from Eq. 2, and then V 2 from Eq. 3. It is found that the resulting V 1 , V 2 , V 3 trio does not satisfy Eq. 1 for any value of V 1 assumed. There is no solution to Eqs. 1, 2, and 3 with real, positive values of V 1 , V 2 , and V 3 . Thus, our original assumption of flow out of reservoir B must be incorrect. To obtain the solution, assume the fluid flows into reservoirs B and C and out of A. For this case the continuity equation becomes or Application of the energy equation between points A and B and A and C gives and p B g V 2 B 2g z B p C g V 2 C 2g z C f / 2 V 2 2 2 D 2 2g f / 3 V 2 3 3 D 3 2g z B f / 2 V 2 2 2 D 2 2g f / 3 V 2 3 3 D 3 2g 64.4 0.5V 2 2 0.4V 2 3 Q 1 Q 2 Q 3 V 1 V 2 V 3 z A z B f / 1 V 2 1 1 D 1 2g f / 2 V 2 2 2 D 2 2g z A z C f / 1 V 2 1 1 D 1 2g f / 2 3 V 3 3 D 3 2g (3) (4) which, with the given data, become and Equations 4, 5, and 6 can be solved as follows. By subtracting Eq. 5 from 6 we obtain Thus, Eq. 5 can be written as or which, upon squaring both sides, can be written as By using the quadratic formula we can solve for V 2 to obtain either V 2 2 452 or V 2 2 2 8.30. Thus, either V 2 21.3 fts or V 2 2.88 fts. The value V 2 21.3 fts is not a root of the original equations. It is an extra root introduced by squaring Eq. 7, which with V 2 21.3 becomes “1140 1140.” Thus, V 2 2.88 fts and from Eq. 5, V 1 15.9 fts. The corresponding flowrates are and 258 V 2 1 0.5 V 2 2 322 V 2 1 0.4 V 2 3 V 3 2160 1.25V 2 2 258 1V 2 V 3 2 2 0.5V 2 2 1V 2 2160 1.25V 2 22 2 0.5V 2 2 2V 2 2160 1.25V 2 2 98 2.75V 2 2 V 4 2 460 V 2 2 3748 0 Q 1 A 1 V 1 p 4 D2 1V 1 p 4 11 ft22 115.9 fts2 12.5 ft 3 s from A Q 2 A 2 V 2 p 4 D2 2V 2 p 4 11 ft22 12.88 fts2 2.26 ft 3 s into B Q 3 Q 1 Q 2 112.5 2.262 ft 3 s 10.2 ft 3 s into C (5) (6) (7) (Ans) (Ans) (Ans) Note the slight differences in the governing equations depending on the direction of the flow in pipe 122—compare Eqs. 1, 2, and 3 with Eqs. 4, 5, and 6. COMMENT If the friction factors were not given, a trial-anderror procedure similar to that needed for Type II problems 1see Section 8.5.12 would be required. Pipe network problems can be solved using node and loop concepts. The ultimate in multiple pipe systems is a network of pipes such as that shown in Fig. 8.38. Networks like these often occur in city water distribution systems and other systems that may have multiple “inlets” and “outlets.” The direction of flow in the various pipes is by no means obvious—in fact, it may vary in time, depending on how the system is used from time to time. The solution for pipe network problems is often carried out by use of node and loop equations similar in many ways to that done in electrical circuits. For example, the continuity equation requires that for each node 1the junction of two or more pipes2 the net flowrate is zero. What flows into a node must flow out at the same rate. In addition, the net pressure difference completely around a loop 1starting at one location in a pipe and returning to that location2 must be zero. By combining these ideas with the usual head loss and pipe flow equations, the flow throughout the entire network can
8.6 Pipe Flowrate Measurement 441 F I G U R E 8.38 pipe network. A general be obtained. Of course, trial-and-error solutions are usually required because the direction of flow and the friction factors may not be known. Such a solution procedure using matrix techniques is ideally suited for computer use 1Refs. 21, 222. 8.6 Pipe Flowrate Measurement It is often necessary to determine experimentally the flowrate in a pipe. In Chapter 3 we introduced various types of flow-measuring devices 1Venturi meter, nozzle meter, orifice meter, etc.2 and discussed their operation under the assumption that viscous effects were not important. In this section we will indicate how to account for the ever-present viscous effects in these flow meters. We will also indicate other types of commonly used flow meters. Orifice, nozzle and Venturi meters involve the concept “high velocity gives low pressure.” 8.6.1 Pipe Flowrate Meters Three of the most common devices used to measure the instantaneous flowrate in pipes are the orifice meter, the nozzle meter, and the Venturi meter. As was discussed in Section 3.6.3, each of these meters operates on the principle that a decrease in flow area in a pipe causes an increase in velocity that is accompanied by a decrease in pressure. Correlation of the pressure difference with the velocity provides a means of measuring the flowrate. In the absence of viscous effects and under the assumption of a horizontal pipe, application of the Bernoulli equation 1Eq. 3.72 between points 112 and 122 shown in Fig. 8.39 gave Q ideal A 2 V 2 A 2 B 21 p 1 p 2 2 r11 b 4 2 (8.37) where b D 2D 1 . Based on the results of the previous sections of this chapter, we anticipate that there is a head loss between 112 and 122 so that the governing equations become and Q A 1 V 1 A 2 V 2 p 1 g V 2 1 2g p 2 g V 2 2 2g h L The ideal situation has h L 0 and results in Eq. 8.37. The difficulty in including the head loss is that there is no accurate expression for it. The net result is that empirical coefficients are used in the flowrate equations to account for the complex real-world effects brought on by the nonzero viscosity. The coefficients are discussed in this section. Q V 1 D 1 (2) V 2 (1) D 2 F I G U R E 8.39 pipe flow meter geometry. Typical
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440 Chapter 8 ■ Viscous Flow in Pipes<br />
or<br />
322 V 2 1 0.4V 2 3<br />
(2)<br />
where V 1 and V 3 are in fts. Similarly the energy equation for<br />
<strong>fluid</strong> flowing from B and C is<br />
or<br />
For the given conditions this can be written as<br />
Equations 1, 2, and 3 1in terms of the three unknowns V 1 , V 2 , and<br />
V 3 2 are the governing equations for this flow, provided the <strong>fluid</strong> flows<br />
from reservoir B. It turns out, however, that there is no solution for<br />
these equations with positive, real values of the velocities. Although<br />
these equations do not appear to be complicated, there is no simple<br />
way to solve them directly. Thus, a trial-and-error solution is suggested.<br />
This can be accomplished as follows. Assume a value of<br />
V 1 7 0, calculate V 3 from Eq. 2, and then V 2 from Eq. 3. It is found<br />
that the resulting V 1 , V 2 , V 3 trio does not satisfy Eq. 1 for any value of<br />
V 1 assumed. There is no solution to Eqs. 1, 2, and 3 with real, positive<br />
values of V 1 , V 2 , and V 3 . Thus, our original assumption of flow out of<br />
reservoir B must be incorrect.<br />
To obtain the solution, assume the <strong>fluid</strong> flows into reservoirs<br />
B and C and out of A. For this case the continuity equation<br />
becomes<br />
or<br />
Application of the energy equation between points A and B and A<br />
and C gives<br />
and<br />
p B<br />
g V 2 B<br />
2g z B p C<br />
g V 2 C<br />
2g z C f / 2 V 2 2<br />
2<br />
D 2 2g f / 3 V 2 3<br />
3<br />
D 3 2g<br />
z B f / 2 V 2 2<br />
2<br />
D 2 2g f / 3 V 2 3<br />
3<br />
D 3 2g<br />
64.4 0.5V 2 2 0.4V 2 3<br />
Q 1 Q 2 Q 3<br />
V 1 V 2 V 3<br />
z A z B f / 1 V 2 1<br />
1<br />
D 1 2g f / 2 V 2 2<br />
2<br />
D 2 2g<br />
z A z C f / 1 V 2 1<br />
1<br />
D 1 2g f / 2<br />
3 V 3<br />
3<br />
D 3 2g<br />
(3)<br />
(4)<br />
which, with the given data, become<br />
and<br />
Equations 4, 5, and 6 can be solved as follows. By subtracting<br />
Eq. 5 from 6 we obtain<br />
Thus, Eq. 5 can be written as<br />
or<br />
which, upon squaring both sides, can be written as<br />
By using the quadratic formula we can solve for V 2 to obtain<br />
either V 2 2 452 or V 2 2<br />
2 8.30. Thus, either V 2 21.3 fts or<br />
V 2 2.88 fts. The value V 2 21.3 fts is not a root of the original<br />
equations. It is an extra root introduced by squaring Eq. 7, which<br />
with V 2 21.3 becomes “1140 1140.” Thus, V 2 2.88 fts<br />
and from Eq. 5, V 1 15.9 fts. The corresponding flowrates are<br />
and<br />
258 V 2 1 0.5 V 2 2<br />
322 V 2 1 0.4 V 2 3<br />
V 3 2160 1.25V 2 2<br />
258 1V 2 V 3 2 2 0.5V 2 2<br />
1V 2 2160 1.25V 2 22 2 0.5V 2 2<br />
2V 2 2160 1.25V 2 2 98 2.75V 2 2<br />
V 4 2 460 V 2 2 3748 0<br />
Q 1 A 1 V 1 p 4 D2 1V 1 p 4 11 ft22 115.9 fts2<br />
12.5 ft 3 s from A<br />
Q 2 A 2 V 2 p 4 D2 2V 2 p 4 11 ft22 12.88 fts2<br />
2.26 ft 3 s into B<br />
Q 3 Q 1 Q 2 112.5 2.262 ft 3 s<br />
10.2 ft 3 s into C<br />
(5)<br />
(6)<br />
(7)<br />
(Ans)<br />
(Ans)<br />
(Ans)<br />
Note the slight differences in the governing equations depending<br />
on the direction of the flow in pipe 122—compare Eqs. 1, 2, and 3<br />
with Eqs. 4, 5, and 6.<br />
COMMENT If the friction factors were not given, a trial-anderror<br />
procedure similar to that needed for Type II problems 1see<br />
Section 8.5.12 would be required.<br />
Pipe network problems<br />
can be solved<br />
using node and<br />
loop concepts.<br />
The ultimate in multiple pipe systems is a network of pipes such as that shown in Fig. 8.38.<br />
Networks like these often occur in city water distribution systems and other systems that may have<br />
multiple “inlets” and “outlets.” The direction of flow in the various pipes is by no means obvious—in<br />
fact, it may vary in time, depending on how the system is used from time to time.<br />
The solution for pipe network problems is often carried out by use of node and loop equations<br />
similar in many ways to that done in electrical circuits. For example, the continuity equation requires<br />
that for each node 1the junction of two or more pipes2 the net flowrate is zero. What flows into a node<br />
must flow out at the same rate. In addition, the net pressure difference completely around a loop<br />
1starting at one location in a pipe and returning to that location2 must be zero. By combining these<br />
ideas with the usual head loss and pipe flow equations, the flow throughout the entire network can