fluid_mechanics
600 Chapter 11 ■ Compressible Flow Finally from Eq. 1 we have (Ans) (b) For p re 40 kPa1abs2 53.3 kPa1abs2 p*, we have p th p* 53.3 kPa1abs2 and Ma th 1. The converging duct is choked. From Eq. 2 1see also Eq. 11.662 or From Eq. 5 1see also Eq. 11.642, or m # 11.04 kgm 3 211 10 4 m 2 21193 ms2 0.0201 kgs r th 1.23 kgm 3 e 1 1 311.4 1224112 2 f 111.412 r th 0.780 kgm 3 T th 288 K 1 1 311.4 1224112 2 T th 240 K From Eq. 4, V th 112 23286.9 J1kg # K241240 K211.42 310 1Jkg2 12 310 ms since 1 Jkg 1 N # mkg 1 1kg # ms 2 2 # mkg 1ms2 2 . Finally from Eq. 1 m # 10.780 kgm 3 211 10 4 m 2 21310 ms2 0.0242 kgs (Ans) From the values of throat temperature and throat pressure calculated above for flow situations 1a2 and 1b2, we can construct the temperature–entropy diagram shown in Fig. E11.5b. COMMENT Note that the flow from standard atmosphere to the receiver for receiver pressure, p re , greater than or equal to the critical pressure, p*, is isentropic. When the receiver pressure is less than the critical pressure as in situation 1b2 above, what is the flow like downstream from the exit of the converging duct? Experience suggests that this flow, when p re 6 p*, is threedimensional and nonisentropic and involves a drop in pressure from p th to p re , a drop in temperature, and an increase of entropy as are indicated in Fig. E11.5c. Isentropic flow Eqs. 11.56, 11.59, and 11.60 have been used to construct Fig. D.1 in Appendix D for air 1k 1.42. Examples 11.6 and 11.7 illustrate how these graphs of TT 0 , pp 0 , and rr 0 as a function of Mach number, Ma, can be used to solve compressible flow problems. E XAMPLE 11.6 Use of Compressible Flow Graphs in Solving Problems GIVEN Consider the flow described in Example 11.5. duct throat to solve for mass flowrate from m # r th A th V th (1) T th 10.9421288 K2 271 K FIND Solve Example 11.5 using Fig. D.1 of Appendix D. SOLUTION We still need the density and velocity of the air at the converging Thus, from Eqs. 2 and 3 (a) Since the receiver pressure, p re 80 kPa1abs2, is greater and than the critical pressure, p* 53.3 kPa1abs2, the throat pressure, r th 10.85211.23 kgm 3 2 1.04 kgm 3 p th , is equal to the receiver pressure. Thus Furthermore, using Eqs. 11.36 and 11.46 we get p th 80 kPa1abs2 p 0 101 kPa1abs2 0.792 From Fig. D.1, for pp 0 0.79, we get from the graph Ma th 0.59 T th 0.94 T 0 r th 0.85 r 0 (2) (3) V th Ma th 2RT th k 10.592 23286.9 J1kg # K241269 K211.42 194 1Jkg2 12 194 ms since 1 Jkg 1 N # mkg 1 1kg # ms 2 2 # mkg 1ms2 2 . Finally, from Eq. 1 m # 11.04 kgm 3 211 10 4 m 2 21194 ms2 0.0202 kgs (Ans)
11.4 Isentropic Flow of an Ideal Gas 601 (b) For p re 40 kPa1abs2 6 53.3 kPa1abs2 p*, the throat pressure is equal to 53.3 kPa1abs2 and the duct is choked with Ma th 1. From Fig. D.1, for Ma 1 we get and From Eqs. 4 and 5 we obtain and T th T 0 0.83 r th r 0 0.64 T th 10.8321288 K2 240 K r th 10.64211.23 kgm 3 2 0.79 kgm 3 (4) (5) Also, from Eqs. 11.36 and 11.46 we conclude that Then, from Eq. 1 V th Ma th 2RT th k 112 23286.9 J1kg # K241240 K211.42 310 1Jkg2 12 310 ms m # 10.79 kgm 3 211 10 4 m 2 21310 ms2 0.024 kgs (Ans) COMMENT The values from Fig. D.1 resulted in answers for mass flowrate that are close to those using the ideal gas equations 1see Example 11.52. The temperature–entropy diagrams remain the same as those provided in the solution of Example 11.5. E XAMPLE 11.7 Static to Stagnation Pressure Ratio GIVEN The static pressure to stagnation pressure ratio at a point in a flow stream is measured with a Pitot-static tube 1see Fig. 3.62 as being equal to 0.82. The stagnation temperature of the fluid is 68 °F. Determine the flow velocity if the fluid is 1a2 air, 1b2 he- FIND lium. SOLUTION We consider both air and helium, flowing as described above, to act as ideal gases with constant specific heats. Then, we can use any of the ideal gas relationships developed in this chapter. To determine the flow velocity, we can combine Eqs. 11.36 and 11.46 to obtain By knowing the value of static to stagnation pressure ratio, pp 0 , and the specific heat ratio we can obtain the corresponding Mach number from Eq. 11.59, or for air, from Fig. D.1. Figure D.1 cannot be used for helium, since k for helium is 1.66 and Fig. D.1 is for k 1.4 only. With Mach number, specific heat ratio, and stagnation temperature known, the value of static temperature can be subsequently ascertained from Eq. 11.56 1or Fig. D.1 for air2. (a) For air, pp 0 0.82; thus from Fig. D.1, and Then, from Eq. 3 V Ma 2RTk Ma 0.54 T T 0 0.94 T 10.9423168 4602 °R4 496 °R (1) (2) (3) (4) and using Eqs. 1, 2, and 4 we get Thus, since 1 lb 32.2 lbm # fts 2 , it follows that (Ans) (b) For helium, pp 0 0.82 and k 1.66. By substituting these values into Eq. 11.59 we get or From Eq. 11.56 we obtain Thus, V 10.542 2353.3 1ft # lb21lbm # °R241496 °R211.42 104 1ft # lblbm2 1 2 V 104 1ft # lblbm2 1 2 3132.2 lbm # fts 2 2lb4 1 2 590 fts 1.6611.6612 1 0.82 e 1 311.66 1224 Ma f 2 T T 0 Ma 0.499 1 1 31k 1224Ma 2 1 T e f3168 4602 °R4 2 1 311.66 122410.4992 488 °R
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600 Chapter 11 ■ Compressible Flow<br />
Finally from Eq. 1 we have<br />
(Ans)<br />
(b) For p re 40 kPa1abs2 53.3 kPa1abs2 p*, we have<br />
p th p* 53.3 kPa1abs2 and Ma th 1. The converging duct is<br />
choked. From Eq. 2 1see also Eq. 11.662<br />
or<br />
From Eq. 5 1see also Eq. 11.642,<br />
or<br />
m # 11.04 kgm 3 211 10 4 m 2 21193 ms2<br />
0.0201 kgs<br />
r th<br />
1.23 kgm 3 e 1<br />
1 311.4 1224112 2 f 111.412<br />
r th 0.780 kgm 3<br />
T th<br />
288 K 1<br />
1 311.4 1224112 2<br />
T th 240 K<br />
From Eq. 4,<br />
V th 112 23286.9 J1kg # K241240 K211.42<br />
310 1Jkg2 12 310 ms<br />
since 1 Jkg 1 N # mkg 1 1kg # ms 2 2 # mkg 1ms2 2 . Finally<br />
from Eq. 1<br />
m # 10.780 kgm 3 211 10 4 m 2 21310 ms2<br />
0.0242 kgs<br />
(Ans)<br />
From the values of throat temperature and throat pressure calculated<br />
above for flow situations 1a2 and 1b2, we can construct the<br />
temperature–entropy diagram shown in Fig. E11.5b.<br />
COMMENT Note that the flow from standard atmosphere to<br />
the receiver for receiver pressure, p re , greater than or equal to the<br />
critical pressure, p*, is isentropic. When the receiver pressure is<br />
less than the critical pressure as in situation 1b2 above, what is the<br />
flow like downstream from the exit of the converging duct? Experience<br />
suggests that this flow, when p re 6 p*, is threedimensional<br />
and nonisentropic and involves a drop in pressure<br />
from p th to p re , a drop in temperature, and an increase of entropy<br />
as are indicated in Fig. E11.5c.<br />
Isentropic flow Eqs. 11.56, 11.59, and 11.60 have been used to construct Fig. D.1 in Appendix<br />
D for air 1k 1.42. Examples 11.6 and 11.7 illustrate how these graphs of TT 0 , pp 0 , and rr 0<br />
as a function of Mach number, Ma, can be used to solve compressible flow problems.<br />
E XAMPLE 11.6<br />
Use of Compressible Flow Graphs in Solving Problems<br />
GIVEN Consider the flow described in Example 11.5.<br />
duct throat to solve for mass flowrate from<br />
m # r th A th V th (1)<br />
T th 10.9421288 K2 271 K<br />
FIND Solve Example 11.5 using Fig. D.1 of Appendix D.<br />
SOLUTION<br />
We still need the density and velocity of the air at the converging Thus, from Eqs. 2 and 3<br />
(a) Since the receiver pressure, p re 80 kPa1abs2, is greater<br />
and<br />
than the critical pressure, p* 53.3 kPa1abs2, the throat pressure,<br />
r th 10.85211.23 kgm 3 2 1.04 kgm 3<br />
p th , is equal to the receiver pressure. Thus<br />
Furthermore, using Eqs. 11.36 and 11.46 we get<br />
p th 80 kPa1abs2<br />
<br />
p 0 101 kPa1abs2 0.792<br />
From Fig. D.1, for pp 0 0.79, we get from the graph<br />
Ma th 0.59<br />
T th<br />
0.94<br />
T 0<br />
r th<br />
0.85<br />
r 0<br />
(2)<br />
(3)<br />
V th Ma th 2RT th k<br />
10.592 23286.9 J1kg # K241269 K211.42<br />
194 1Jkg2 12 194 ms<br />
since 1 Jkg 1 N # mkg 1 1kg # ms 2 2 # mkg 1ms2 2 . Finally,<br />
from Eq. 1<br />
m # 11.04 kgm 3 211 10 4 m 2 21194 ms2<br />
0.0202 kgs<br />
(Ans)