fluid_mechanics
230 Chapter 5 ■ Finite Control Volume Analysis where is the heat transfer rate per mass flowrate, or heat transfer per unit mass. Note that Eq. 5.73 involves energy per unit mass and is applicable to one-dimensional flow of a single stream of fluid between two sections or flow along a streamline between two sections. If the steady, incompressible flow we are considering also involves negligible viscous effects 1frictionless flow2, then the Bernoulli equation, Eq. 3.7, can be used to describe what happens between two sections in the flow as p out rV 2 out 2 q net in Q# net in m # gz out p in rV 2 in 2 gz in (5.74) where g rg is the specific weight of the fluid. To get Eq. 5.74 in terms of energy per unit mass, so that it can be compared directly with Eq. 5.73, we divide Eq. 5.74 by density, r, and obtain Minimizing loss is the central goal of fluid mechanical design. p out r V 2 out 2 gz out p in r V 2 in 2 gz in A comparison of Eqs. 5.73 and 5.75 prompts us to conclude that (5.75) ǔ out ǔ in q net 0 (5.76) in when the steady incompressible flow is frictionless. For steady incompressible flow with friction, we learn from experience (second law of thermodynamics) that ǔ out ǔ in q net 7 0 in In Eqs. 5.73 and 5.75, we can consider the combination of variables p r V 2 2 gz (5.77) as equal to useful or available energy. Thus, from inspection of Eqs. 5.73 and 5.75, we can conclude that ǔ out ǔ in q net in represents the loss of useful or available energy that occurs in an incompressible fluid flow because of friction. In equation form we have ǔ out ǔ in q net in loss For a frictionless flow, Eqs. 5.73 and 5.75 tell us that loss equals zero. It is often convenient to express Eq. 5.73 in terms of loss as (5.78) p out r V 2 out 2 gz out p in r V 2 in 2 gz in loss An example of the application of Eq. 5.79 follows. (5.79) E XAMPLE 5.23 Energy—Effect of Loss of Available Energy GIVEN As shown in Fig. E5.23a, air flows from a room through two different vent configurations: a cylindrical hole in the wall having a diameter of 120 mm and the same diameter cylindrical hole in the wall but with a well-rounded entrance. The room pressure is held constant at 1.0 kPa above atmospheric pressure. Both vents exhaust into the atmosphere. As discussed in Section 8.4.2, the loss in available energy associated with flow through the cylindrical vent from the room to the vent exit is 0.5V 2 2/2 where V 2 is the uniformly distributed exit velocity of air. The loss in available energy associated with flow through the rounded entrance vent from the room to the vent exit is 0.05V 2 2/2, where V 2 is the uniformly distributed exit velocity of air. FIND Compare the volume flowrates associated with the two different vent configurations.
5.3 First Law of Thermodynamics — The Energy Equation 231 SOLUTION We use the control volume for each vent sketched in Fig. E5.23a. What is sought is the flowrate, Q A 2 V 2 , where A 2 is the vent exit cross-sectional area, and V 2 is the uniformly distributed exit velocity. For both vents, application of Eq. 5.79 leads to 0 (no elevation change) p 2 V 2 2 2 gz 2 p 1 V 2 1 2 gz 1 1 loss 2 0 1V 1 02 where 1 loss 2 is the loss between sections (1) and (2). Solving Eq. 1 for V 2 we get (1) Control volume Section (1) for both vents is in the room and involves V 1 = 0 p 1 = 1.0 kPa D 2 = 120 mm D 2 = 120 mm V 2 Section (2) V 2 Section (2) V 2 2 ca p 1 p 2 b B 1 loss 2 d (2) Control volume Since 1loss 2 K L V 2 2 2 (3) F I G U R E E5.23a where K L is the loss coefficient (K L 0.5 and 0.05 for the two vent configurations involved), we can combine Eqs. 2 and 3 to get Solving Eq. 4 for V 2 we obtain Therefore, for flowrate, Q, we obtain For the rounded entrance cylindrical vent, Eq. 6 gives or Q A 2 V 2 pD 2 2 p 1 p 2 4 B r311 K L 224 p1120 mm22 Q 411000 mmm2 2 V 2 2 ca p 1 p 2 b K V 2 2 B L 2 d 11.0 kPa211000 PakPa2311Nm 2 21Pa24 B 11.23 kgm 3 2311 0.05224311Ns 2 21kgm24 For the cylindrical vent, Eq. 6 gives us p1120 mm22 Q 411000 mmm2 2 V 2 B p 1 p 2 r311 K L 224 Q 0.445 m 3 /s 11.0 kPa211000 PakPa2311Nm 2 21Pa24 B 11.23 kgm 3 2311 0.5224311Ns 2 21kgm24 (4) (5) (6) (Ans) or Q 0.372 m 3 /s (Ans) COMMENT By repeating the calculations for various values of the loss coefficient, K L , the results shown in Fig. E5.23b are obtained. Note that the rounded entrance vent allows the passage of more air than does the cylindrical vent because the loss associated with the rounded entrance vent is less than that for the cylindrical one. For this flow the pressure drop, p 1 p 2 , has two purposes: (1) overcome the loss associated with the flow, and (2) produce the kinetic energy at the exit. Even if there were no loss (i.e., K L 0), a pressure drop would be needed to accelerate the fluid through the vent. Q, m 3 /s 0.5 0.4 0.3 0.2 0.1 (0.05, 0.445 m 3 /s) 0 0 0.1 0.2 0.3 0.4 0.5 K L F I G U R E E5.23b (0.5, 0.372 m 3 /s) An important group of fluid mechanics problems involves one-dimensional, incompressible, steady-in-the-mean flow with friction and shaft work. Included in this category are constant density flows through pumps, blowers, fans, and turbines. For this kind of flow, Eq. 5.67 becomes m # c ǔ out ǔ in p out r p in r V 2 out V 2 in g1z 2 out z in 2d Q # net W # shaft in net in (5.80)
- Page 204 and 205: 180 Chapter 4 ■ Fluid Kinematics
- Page 206 and 207: 182 Chapter 4 ■ Fluid Kinematics
- Page 208 and 209: 184 Chapter 4 ■ Fluid Kinematics
- Page 210 and 211: 186 Chapter 4 ■ Fluid Kinematics
- Page 212 and 213: 188 Chapter 5 ■ Finite Control Vo
- Page 214 and 215: 190 Chapter 5 ■ Finite Control Vo
- Page 216 and 217: 192 Chapter 5 ■ Finite Control Vo
- Page 218 and 219: 194 Chapter 5 ■ Finite Control Vo
- Page 220 and 221: 196 Chapter 5 ■ Finite Control Vo
- Page 222 and 223: 198 Chapter 5 ■ Finite Control Vo
- Page 224 and 225: 200 Chapter 5 ■ Finite Control Vo
- Page 226 and 227: 202 Chapter 5 ■ Finite Control Vo
- Page 228 and 229: 204 Chapter 5 ■ Finite Control Vo
- Page 230 and 231: 206 Chapter 5 ■ Finite Control Vo
- Page 232 and 233: 208 Chapter 5 ■ Finite Control Vo
- Page 234 and 235: 210 Chapter 5 ■ Finite Control Vo
- Page 236 and 237: 212 Chapter 5 ■ Finite Control Vo
- Page 238 and 239: 214 Chapter 5 ■ Finite Control Vo
- Page 240 and 241: 216 Chapter 5 ■ Finite Control Vo
- Page 242 and 243: 218 Chapter 5 ■ Finite Control Vo
- Page 244 and 245: 220 Chapter 5 ■ Finite Control Vo
- Page 246 and 247: 222 Chapter 5 ■ Finite Control Vo
- Page 248 and 249: 224 Chapter 5 ■ Finite Control Vo
- Page 250 and 251: 226 Chapter 5 ■ Finite Control Vo
- Page 252 and 253: 228 Chapter 5 ■ Finite Control Vo
- Page 256 and 257: 232 Chapter 5 ■ Finite Control Vo
- Page 258 and 259: 234 Chapter 5 ■ Finite Control Vo
- Page 260 and 261: 236 Chapter 5 ■ Finite Control Vo
- Page 262 and 263: 238 Chapter 5 ■ Finite Control Vo
- Page 264 and 265: 240 Chapter 5 ■ Finite Control Vo
- Page 266 and 267: 242 Chapter 5 ■ Finite Control Vo
- Page 268 and 269: 244 Chapter 5 ■ Finite Control Vo
- Page 270 and 271: 246 Chapter 5 ■ Finite Control Vo
- Page 272 and 273: 248 Chapter 5 ■ Finite Control Vo
- Page 274 and 275: 250 Chapter 5 ■ Finite Control Vo
- Page 276 and 277: 252 Chapter 5 ■ Finite Control Vo
- Page 278 and 279: 254 Chapter 5 ■ Finite Control Vo
- Page 280 and 281: 256 Chapter 5 ■ Finite Control Vo
- Page 282 and 283: 258 Chapter 5 ■ Finite Control Vo
- Page 284 and 285: 260 Chapter 5 ■ Finite Control Vo
- Page 286 and 287: 262 Chapter 5 ■ Finite Control Vo
- Page 288 and 289: 264 Chapter 6 ■ Differential Anal
- Page 290 and 291: ) 266 Chapter 6 ■ Differential An
- Page 292 and 293: 268 Chapter 6 ■ Differential Anal
- Page 294 and 295: 270 Chapter 6 ■ Differential Anal
- Page 296 and 297: 272 Chapter 6 ■ Differential Anal
- Page 298 and 299: 274 Chapter 6 ■ Differential Anal
- Page 300 and 301: 276 Chapter 6 ■ Differential Anal
- Page 302 and 303: 278 Chapter 6 ■ Differential Anal
5.3 First Law of Thermodynamics — The Energy Equation 231<br />
SOLUTION<br />
We use the control volume for each vent sketched in Fig. E5.23a.<br />
What is sought is the flowrate, Q A 2 V 2 , where A 2 is the vent exit<br />
cross-sectional area, and V 2 is the uniformly distributed exit velocity.<br />
For both vents, application of Eq. 5.79 leads to<br />
0 (no elevation change)<br />
p 2<br />
V 2 2<br />
2 gz 2 p 1<br />
V 2 1<br />
2 gz 1 1 loss 2<br />
0 1V 1 02<br />
where 1 loss 2 is the loss between sections (1) and (2). Solving Eq.<br />
1 for V 2 we get<br />
(1)<br />
Control<br />
volume<br />
Section (1) for<br />
both vents is<br />
in the room and<br />
involves V 1 = 0<br />
p 1 = 1.0 kPa<br />
D 2 = 120 mm<br />
D 2 = 120 mm<br />
V 2<br />
Section (2)<br />
V 2<br />
Section (2)<br />
V 2 2 ca p 1 p 2<br />
b B 1 loss 2 d<br />
(2)<br />
Control<br />
volume<br />
Since<br />
1loss 2 K L V 2 2<br />
2<br />
(3)<br />
F I G U R E E5.23a<br />
where K L is the loss coefficient (K L 0.5 and 0.05 for the two vent<br />
configurations involved), we can combine Eqs. 2 and 3 to get<br />
Solving Eq. 4 for V 2 we obtain<br />
Therefore, for flowrate, Q, we obtain<br />
For the rounded entrance cylindrical vent, Eq. 6 gives<br />
or<br />
Q A 2 V 2 pD 2 2 p 1 p 2<br />
4 B r311 K L 224<br />
p1120 mm22<br />
Q <br />
411000 mmm2 2<br />
V 2 2 ca p 1 p 2<br />
b K V 2 2<br />
B <br />
L<br />
2 d<br />
11.0 kPa211000 PakPa2311Nm 2 21Pa24<br />
B 11.23 kgm 3 2311 0.05224311Ns 2 21kgm24<br />
For the cylindrical vent, Eq. 6 gives us<br />
p1120 mm22<br />
Q <br />
411000 mmm2 2<br />
V 2 B<br />
p 1 p 2<br />
r311 K L 224<br />
Q 0.445 m 3 /s<br />
11.0 kPa211000 PakPa2311Nm 2 21Pa24<br />
B 11.23 kgm 3 2311 0.5224311Ns 2 21kgm24<br />
(4)<br />
(5)<br />
(6)<br />
(Ans)<br />
or<br />
Q 0.372 m 3 /s<br />
(Ans)<br />
COMMENT By repeating the calculations for various values<br />
of the loss coefficient, K L , the results shown in Fig. E5.23b are<br />
obtained. Note that the rounded entrance vent allows the passage<br />
of more air than does the cylindrical vent because the loss associated<br />
with the rounded entrance vent is less than that for the<br />
cylindrical one. For this flow the pressure drop, p 1 p 2 , has two<br />
purposes: (1) overcome the loss associated with the flow, and (2)<br />
produce the kinetic energy at the exit. Even if there were no loss<br />
(i.e., K L 0), a pressure drop would be needed to accelerate the<br />
<strong>fluid</strong> through the vent.<br />
Q, m 3 /s<br />
0.5<br />
0.4<br />
0.3<br />
0.2<br />
0.1<br />
(0.05, 0.445 m 3 /s)<br />
0<br />
0 0.1 0.2 0.3 0.4 0.5<br />
K L<br />
F I G U R E E5.23b<br />
(0.5, 0.372 m 3 /s)<br />
An important group of <strong>fluid</strong> <strong>mechanics</strong> problems involves one-dimensional, incompressible,<br />
steady-in-the-mean flow with friction and shaft work. Included in this category are constant density<br />
flows through pumps, blowers, fans, and turbines. For this kind of flow, Eq. 5.67 becomes<br />
m # c ǔ out ǔ in p out<br />
r p in<br />
r V 2 out V 2 in<br />
g1z<br />
2<br />
out z in 2d Q # net W # shaft<br />
in net in<br />
(5.80)