fluid_mechanics
398 Chapter 8 ■ Viscous Flow in Pipes E XAMPLE 8.3 Laminar Pipe Flow Properties GIVEN The flowrate, Q, of corn syrup through the horizontal pipe shown in Fig. E8.3a is to be monitored by measuring the pressure difference between sections 112 and 122. It is proposed that Q K ¢p, where the calibration constant, K, is a function of temperature, T, because of the variation of the syrup’s viscosity and density with temperature. These variations are given in Table E8.3. FIND (a) Plot K1T 2 versus T for 60 °F T 160 °F. (b) Determine the wall shear stress and the pressure drop, ¢p p for Q 0.5 ft 3 1 p 2 , s and T 100 °F. (c) For the conditions of part 1b2, determine the net pressure force, 1pD 2 42 ¢p, and the net shear force, pD/t w , on the fluid within the pipe between the sections 112 and 122. SOLUTION (a) or If the flow is laminar it follows from Eq. 8.9 that where the units on Q, ¢p, and m are ft 3 s, lbft 2 , and lb # sft 2 , respectively. Thus (1) (Ans) where the units of K are ft 5 lb # s. By using values of the viscosity from Table E8.3, the calibration curve shown in Fig. E8.3b is obtained. This result is valid only if the flow is laminar. COMMENT As shown in Section 8.5, for turbulent flow the flowrate is not linearly related to the pressure drop so it would not be possible to have Q K ¢p. Note also that the value of K is independent of the syrup density 1r was not used in the calculations2 since laminar pipe flow is governed by pressure and viscous effects; inertia is not important. (b) For T 100 °F, the viscosity is m 3.8 10 3 lb # sft 2 so that with a flowrate of Q 0.5 ft 3 s the pressure drop 1according to Eq. 8.92 is 12813.8 103 lb # sft 2 216 ft210.5 ft 3 s2 p1 3 12 ft2 4 119 lbft 2 provided the flow is laminar. For this case so that ¢p 128m/Q pD 4 Q pD4 ¢p 128m/ p1 3 12 ft2 4 ¢p 128m16 ft2 Q K ¢p K V Q A 0.5 ft3 s 10.2 fts p 4 1 3 12 ft2 2 Re rVD m 12.05 slugs ft 3 2110.2 fts21 3 12 ft2 13.8 10 3 lb # sft 2 2 1380 6 2100 1.60 105 ¢p m 1.60 105 m (Ans) Q is K, ft 5 /(lb • s) 10 0 10 –1 10 –2 10 –3 (1) F I G U R E E8.3 TABLE E8.3 T ( F) R (slugs ft 3 ) M ( lb sft 2 ) 60 2.07 4.0 10 2 80 2.06 1.9 10 2 100 2.05 3.8 10 3 120 2.04 4.4 10 4 140 2.03 9.2 10 5 160 2.02 2.3 10 5 Hence, the flow is laminar. From Eq. 8.5 the wall shear stress t w ¢pD 4/ 1119 lb ft 2 21 3 12 ft2 1.24 lbft 2 416 ft2 (Ans) (c) For the conditions of part 1b2, the net pressure force, F p , on the fluid within the pipe between sections 112 and 122 is F p p 4 D2 ¢p p 4 a 3 12 ftb 2 1119 lbft 2 2 5.84 lb (Ans) Similarly, the net viscous force, F v , on that portion of the fluid is F v 2p a D 2 b /t w 6 ft (a) 10 –4 60 100 140 T, °F (b) (2) 3-in. diameter 180 3 2p c 21122 ft d16 ft211.24 lb ft 2 2 5.84 lb (Ans) COMMENT Note that the values of these two forces are the same. The net force is zero; there is no acceleration.
8.3 Fully Developed Turbulent Flow 399 8.3 Fully Developed Turbulent Flow In the previous section various properties of fully developed laminar pipe flow were discussed. Since turbulent pipe flow is actually more likely to occur than laminar flow in practical situations, it is necessary to obtain similar information for turbulent pipe flow. However, turbulent flow is a very complex process. Numerous persons have devoted considerable effort in attempting to understand the variety of baffling aspects of turbulence. Although a considerable amount of knowledge about the topic has been developed, the field of turbulent flow still remains the least understood area of fluid mechanics. In this book we can provide only some of the very basic ideas concerning turbulence. The interested reader should consult some of the many books available for further reading 1Refs. 1–32. Turbulent flows involve randomly fluctuating parameters. 8.3.1 Transition from Laminar to Turbulent Flow Flows are classified as laminar or turbulent. For any flow geometry, there is one 1or more2 dimensionless parameter such that with this parameter value below a particular value the flow is laminar, whereas with the parameter value larger than a certain value the flow is turbulent. The important parameters involved 1i.e., Reynolds number, Mach number2 and their critical values depend on the specific flow situation involved. For example, flow in a pipe and flow along a flat plate 1boundary layer flow, as is discussed in Section 9.2.42 can be laminar or turbulent, depending on the value of the Reynolds number involved. As a general rule for pipe flow, the value of the Reynolds number must be less than approximately 2100 for laminar flow and greater than approximately 4000 for turbulent flow. For flow along a flat plate the transition between laminar and turbulent flow occurs at a Reynolds number of approximately 500,000 1see Section 9.2.42, where the length term in the Reynolds number is the distance measured from the leading edge of the plate. Consider a long section of pipe that is initially filled with a fluid at rest. As the valve is opened to start the flow, the flow velocity and, hence, the Reynolds number increase from zero 1no flow2 to their maximum steady-state flow values, as is shown in Fig. 8.11. Assume this transient process is slow enough so that unsteady effects are negligible 1quasi-steady flow2. For an initial time period the Reynolds number is small enough for laminar flow to occur. At some time the Reynolds number reaches 2100, and the flow begins its transition to turbulent conditions. Intermittent spots or bursts of turbulence appear. As the Reynolds number is increased, the entire flow field becomes turbulent. The flow remains turbulent as long as the Reynolds number exceeds approximately 4000. A typical trace of the axial component of velocity measured at a given location in the flow, u u1t2, is shown in Fig. 8.12. Its irregular, random nature is the distinguishing feature of turbulent flow. The character of many of the important properties of the flow 1pressure drop, heat transfer, etc.2 depends strongly on the existence and nature of the turbulent fluctuations or randomness 3 Random, turbulent fluctuations Turbulent u, ft/s 2 1 Turbulent bursts Laminar Transitional 4000 2000 Re = VD/v 0 0 t, sec F I G U R E 8.11 Transition from laminar to turbulent flow in a pipe.
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398 Chapter 8 ■ Viscous Flow in Pipes<br />
E XAMPLE 8.3<br />
Laminar Pipe Flow Properties<br />
GIVEN The flowrate, Q, of corn syrup through the horizontal<br />
pipe shown in Fig. E8.3a is to be monitored by measuring the pressure<br />
difference between sections 112 and 122. It is proposed that<br />
Q K ¢p, where the calibration constant, K, is a function of temperature,<br />
T, because of the variation of the syrup’s viscosity and<br />
density with temperature. These variations are given in Table E8.3.<br />
FIND (a) Plot K1T 2 versus T for 60 °F T 160 °F. (b) Determine<br />
the wall shear stress and the pressure drop,<br />
¢p p for Q 0.5 ft 3 1 p 2 , s and T 100 °F. (c) For the conditions<br />
of part 1b2, determine the net pressure force, 1pD 2 42 ¢p,<br />
and the net shear force, pD/t w , on the <strong>fluid</strong> within the pipe between<br />
the sections 112 and 122.<br />
SOLUTION<br />
(a)<br />
or<br />
If the flow is laminar it follows from Eq. 8.9 that<br />
where the units on Q, ¢p, and m are ft 3 s, lbft 2 , and lb # sft 2 , respectively.<br />
Thus<br />
(1)<br />
(Ans)<br />
where the units of K are ft 5 lb # s. By using values of the viscosity<br />
from Table E8.3, the calibration curve shown in Fig. E8.3b is obtained.<br />
This result is valid only if the flow is laminar.<br />
COMMENT As shown in Section 8.5, for turbulent flow the<br />
flowrate is not linearly related to the pressure drop so it would not<br />
be possible to have Q K ¢p. Note also that the value of K is independent<br />
of the syrup density 1r<br />
was not used in the calculations2<br />
since laminar pipe flow is governed by pressure and viscous effects;<br />
inertia is not important.<br />
(b) For T 100 °F, the viscosity is m 3.8 10 3 lb # sft 2<br />
so that with a flowrate of Q 0.5 ft 3 s the pressure drop 1according<br />
to Eq. 8.92 is<br />
12813.8 103 lb # sft 2 216 ft210.5 ft 3 s2<br />
p1 3 12 ft2 4<br />
119 lbft 2<br />
provided the flow is laminar. For this case<br />
so that<br />
¢p 128m/Q<br />
pD 4<br />
Q pD4 ¢p<br />
128m/ p1 3<br />
12 ft2 4 ¢p<br />
128m16 ft2<br />
Q K ¢p <br />
K <br />
V Q A 0.5 ft3 s<br />
10.2 fts<br />
p<br />
4 1 3<br />
12 ft2 2<br />
Re rVD<br />
m 12.05 slugs ft 3 2110.2 fts21 3<br />
12 ft2<br />
13.8 10 3 lb # sft 2 2<br />
1380 6 2100<br />
1.60 105<br />
¢p<br />
m<br />
1.60 105<br />
m<br />
(Ans)<br />
Q<br />
is<br />
K, ft 5 /(lb • s)<br />
10 0<br />
10 –1<br />
10 –2<br />
10 –3<br />
(1)<br />
F I G U R E E8.3<br />
TABLE E8.3<br />
T ( F) R (slugs ft 3 ) M ( lb sft 2 )<br />
60 2.07 4.0 10 2<br />
80 2.06 1.9 10 2<br />
100 2.05 3.8 10 3<br />
120 2.04 4.4 10 4<br />
140 2.03 9.2 10 5<br />
160 2.02 2.3 10 5<br />
Hence, the flow is laminar. From Eq. 8.5 the wall shear stress<br />
t w ¢pD<br />
4/ 1119 lb ft 2 21 3 12 ft2<br />
1.24 lbft 2<br />
416 ft2<br />
(Ans)<br />
(c) For the conditions of part 1b2, the net pressure force, F p , on<br />
the <strong>fluid</strong> within the pipe between sections 112 and 122 is<br />
F p p 4 D2 ¢p p 4 a 3<br />
12 ftb 2<br />
1119 lbft 2 2 5.84 lb<br />
(Ans)<br />
Similarly, the net viscous force, F v , on that portion of the <strong>fluid</strong> is<br />
F v 2p a D 2 b /t w<br />
6 ft<br />
(a)<br />
10 –4 60 100 140<br />
T, °F<br />
(b)<br />
(2)<br />
3-in.<br />
diameter<br />
180<br />
3<br />
2p c<br />
21122 ft d16 ft211.24 lb ft 2 2 5.84 lb<br />
(Ans)<br />
COMMENT Note that the values of these two forces are the<br />
same. The net force is zero; there is no acceleration.