fluid_mechanics
662 Chapter 12 ■ Turbomachines Since the only head loss to be considered is the loss a h L K V 2 L 2g with V Q A 0.5 ft 3 s 1p421412 ft2 5.73 ft s 2 it follows that a h L 120215.73 ft s2 2 2132.2 fts 2 2 10.2 ft From Table B.1 the water vapor pressure at 80 °F is 0.5069 psia and g 62.22 lbft 3 . Equation 112 can now be written as 1z 1 2 max 114.7 lb in. 2 21144 in. 2 ft 2 2 62.22 lbft 3 10.2 ft 10.5069 lb in. 2 21144 in. 2 ft 2 2 15 ft 62.22 lbft 3 7.65 ft (Ans) Thus, to prevent cavitation, with its accompanying poor pump performance, the pump should not be located higher than 7.65 ft above the water surface. COMMENT If the valve is placed upstream of the pump, not only would the pump have to operate with an additional loss in the system, it would now operate with a lower inlet pressure because of this additional upstream loss and could now suffer cavitation with its usually negative consequences. If the valve is placed downstream of the pump, the pump would need to operate with more loss in the system and with higher back pressure than without the valve. Depending on the stability of the pump at higher back pressures, this could be inconsequential or important. Usually, pumps are stable even with higher back pressures. So, placing the valve on the downstream side of the pump is normally the better choice. The system equation relates the actual head gained by the fluid to the flowrate. h a 12.4.4 System Characteristics and Pump Selection A typical flow system in which a pump is used is shown in Fig. 12.14. The energy equation applied between points 112 and 122 indicates that h a z 2 z 1 a h L (12.26) where h a is the actual head gained by the fluid from the pump, and h L represents all friction losses in the pipe and minor losses for pipe fittings and valves. From our study of pipe flow, we know that typically h L varies approximately as the flowrate squared; that is, 1see Section 8.42. Thus, Eq. 12.26 can be written in the form h a z 2 z 1 KQ 2 h L Q 2 (12.27) z 2 – z 1 h a = z 2 – z 1 + KQ 2 Q where K depends on the pipe sizes and lengths, friction factors, and minor loss coefficients. Equation 12.27, which is shown in the figure in the margin, is the system equation and shows how the actual head gained by the fluid from the pump is related to the system parameters. In this case the parameters include the change in elevation head, z 2 z 1 , and the losses due to friction as expressed by KQ 2 . Each flow system has its own specific system equation. If the flow is laminar, the frictional losses will be proportional to Q rather than Q 2 1see Section 8.22. (2) (1) z 2 z 1 Pump F I G U R E 12.14 Typical flow system.
12.4 The Centrifugal Pump 663 Change in system equation System curve Pump performance curve (B) (A) Efficiency curve Actual pump head, h a Operating point Efficiency Elevation (static) head = z 2 – z 1 F I G U R E 12.15 Utilization of the system curve and the pump performance curve to obtain the operating point for the Flowrate, Q system. The intersection of the pump performance curve and the system curve is the operating point. There is also a unique relationship between the actual pump head gained by the fluid and the flowrate, which is governed by the pump design 1as indicated by the pump performance curve2. To select a pump for a particular application, it is necessary to utilize both the system curve, as determined by the system equation, and the pump performance curve. If both curves are plotted on the same graph, as illustrated in Fig. 12.15, their intersection 1point A2 represents the operating point for the system. That is, this point gives the head and flowrate that satisfies both the system equation and the pump equation. On the same graph the pump efficiency is shown. Ideally, we want the operating point to be near the best efficiency point 1BEP2 for the pump. For a given pump, it is clear that as the system equation changes, the operating point will shift. For example, if the pipe friction increases due to pipe wall fouling, the system curve changes, resulting in the operating point A shifting to point B in Fig. 12.15 with a reduction in flowrate and efficiency. The following example shows how the system and pump characteristics can be used to decide if a particular pump is suitable for a given application. F l u i d s i n t h e N e w s Space Shuttle fuel pumps The fuel pump of your car engine is vital to its operation. Similarly, the fuels (liquid hydrogen and oxygen) of each Space Shuttle main engine (there are three per shuttle) rely on multistage turbopumps to get from storage tanks to main combustors. High pressures are utilized throughout the pumps to avoid cavitation. The pumps, some centrifugal and some axial, are driven by axial-flow, multistage turbines. Pump speeds are as high as 35,360 rpm. The liquid oxygen is pumped from 100 to 7420 psia, the liquid hydrogen from 30 to 6515 psia. Liquid hydrogen and oxygen flowrates of about 17,200 gpm and 6100 gpm, respectively, are achieved. These pumps could empty your home swimming pool in seconds. The hydrogen goes from 423 °F in storage to 6000 °F in the combustion chamber! E XAMPLE 12.4 Use of Pump Performance Curves GIVEN Water is to be pumped from one large, open tank to a second large, open tank as shown in Fig. E12.4a. The pipe diameter throughout is 6 in. and the total length of the pipe between the pipe entrance and exit is 200 ft. Minor loss coefficients for the entrance, exit, and the elbow are shown, and the friction factor for the pipe can be assumed constant and equal to 0.02. A certain centrifugal pump having the performance characteristics shown in Fig. E12.4b is suggested as a good pump for this flow system. FIND With this pump, what would be the flowrate between the tanks? Do you think this pump would be a good choice?
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12.4 The Centrifugal Pump 663<br />
Change in<br />
system equation<br />
System<br />
curve<br />
Pump performance<br />
curve<br />
(B)<br />
(A)<br />
Efficiency<br />
curve<br />
Actual pump<br />
head, h a<br />
Operating<br />
point<br />
Efficiency<br />
Elevation (static) head<br />
= z 2 – z 1<br />
F I G U R E 12.15 Utilization of<br />
the system curve and the pump performance<br />
curve to obtain the operating point for the<br />
Flowrate, Q<br />
system.<br />
The intersection of<br />
the pump performance<br />
curve and<br />
the system curve is<br />
the operating point.<br />
There is also a unique relationship between the actual pump head gained by the <strong>fluid</strong> and<br />
the flowrate, which is governed by the pump design 1as indicated by the pump performance curve2.<br />
To select a pump for a particular application, it is necessary to utilize both the system curve, as<br />
determined by the system equation, and the pump performance curve. If both curves are plotted<br />
on the same graph, as illustrated in Fig. 12.15, their intersection 1point A2 represents the operating<br />
point for the system. That is, this point gives the head and flowrate that satisfies both the system<br />
equation and the pump equation. On the same graph the pump efficiency is shown. Ideally,<br />
we want the operating point to be near the best efficiency point 1BEP2 for the pump. For a given<br />
pump, it is clear that as the system equation changes, the operating point will shift. For example,<br />
if the pipe friction increases due to pipe wall fouling, the system curve changes, resulting in the<br />
operating point A shifting to point B in Fig. 12.15 with a reduction in flowrate and efficiency.<br />
The following example shows how the system and pump characteristics can be used to decide if<br />
a particular pump is suitable for a given application.<br />
F l u i d s i n t h e N e w s<br />
Space Shuttle fuel pumps The fuel pump of your car engine is<br />
vital to its operation. Similarly, the fuels (liquid hydrogen and<br />
oxygen) of each Space Shuttle main engine (there are three per<br />
shuttle) rely on multistage turbopumps to get from storage<br />
tanks to main combustors. High pressures are utilized throughout<br />
the pumps to avoid cavitation. The pumps, some centrifugal<br />
and some axial, are driven by axial-flow, multistage turbines.<br />
Pump speeds are as high as 35,360 rpm. The liquid oxygen is<br />
pumped from 100 to 7420 psia, the liquid hydrogen from 30 to<br />
6515 psia. Liquid hydrogen and oxygen flowrates of about<br />
17,200 gpm and 6100 gpm, respectively, are achieved. These<br />
pumps could empty your home swimming pool in seconds. The<br />
hydrogen goes from 423 °F in storage to 6000 °F in the<br />
combustion chamber!<br />
E XAMPLE 12.4<br />
Use of Pump Performance Curves<br />
GIVEN Water is to be pumped from one large, open tank to a<br />
second large, open tank as shown in Fig. E12.4a. The pipe<br />
diameter throughout is 6 in. and the total length of the pipe<br />
between the pipe entrance and exit is 200 ft. Minor loss coefficients<br />
for the entrance, exit, and the elbow are shown, and the<br />
friction factor for the pipe can be assumed constant and equal to<br />
0.02. A certain centrifugal pump having the performance characteristics<br />
shown in Fig. E12.4b is suggested as a good pump for<br />
this flow system.<br />
FIND With this pump, what would be the flowrate between the<br />
tanks? Do you think this pump would be a good choice?