fluid_mechanics
226 Chapter 5 ■ Finite Control Volume Analysis m • out m • in dA V Streamtube F I G U R E 5.7 Streamtube flow. Furthermore, if there is only one stream entering and leaving the control volume, then aǔ p cs r V 2 gzb rV nˆ dA 2 aǔ p r V 2 2 gzb m # out aǔ p out r V 2 2 gzb m # in in (5.66) Uniform flow as described above will occur in an infinitesimally small diameter streamtube as illustrated in Fig. 5.7. This kind of streamtube flow is representative of the steady flow of a particle of fluid along a pathline. We can also idealize actual conditions by disregarding nonuniformities in a finite cross section of flow. We call this one-dimensional flow and although such uniform flow rarely occurs in reality, the simplicity achieved with the one-dimensional approximation often justifies its use. More details about the effects of nonuniform distributions of velocities and other fluid flow variables are considered in Section 5.3.4 and in Chapters 8, 9, and 10. If shaft work is involved, the flow must be unsteady, at least locally 1see Refs. 1 and 22. The flow in any fluid machine that involves shaft work is unsteady within that machine. For example, the velocity and pressure at a fixed location near the rotating blades of a fan are unsteady. However, upstream and downstream of the machine, the flow may be steady. Most often shaft work is associated with flow that is unsteady in a recurring or cyclical way. On a time-average basis for flow that is one-dimensional, cyclical, and involves only one stream of fluid entering and leaving the control volume, Eq. 5.64 can be simplified with the help of Eqs. 5.9 and 5.66 to form m # c ǔ out ǔ in a p r b a p out r b in V 2 out V 2 in 2 g1z out z in 2d Q # net in W # shaft net in (5.67) We call Eq. 5.67 the one-dimensional energy equation for steady-in-the-mean flow. Note that Eq. 5.67 is valid for incompressible and compressible flows. Often, the fluid property called enthalpy, ȟ, where (5.68) ȟ ǔ p r The energy equation is sometimes written in terms of enthalpy. is used in Eq. 5.67. With enthalpy, the one-dimensional energy equation for steady-in-the-mean flow 1Eq. 5.672 is m # c ȟ out ȟ in V 2 out V 2 in 2 g1z out z in 2d Q # net in W # shaft net in (5.69) Equation 5.69 is often used for solving compressible flow problems. Examples 5.20 and 5.21 illustrate how Eqs. 5.67 and 5.69 can be used. E XAMPLE 5.20 Energy—Pump Power GIVEN A pump delivers water at a steady rate of 300 gal/min as shown in Fig. E5.20. Just upstream of the pump [section (1)] where the pipe diameter is 3.5 in., the pressure is 18 psi. Just downstream of the pump [section (2)] where the pipe diameter is 1 in., the pressure is 60 psi. The change in water elevation across the pump is zero. The rise in internal energy of water, ǔ 2 ǔ 1 , associated with a temperature rise across the pump is 93 ft lb/lbm. The pumping process is considered to be adiabatic. FIND Determine the power (hp) required by the pump.
5.3 First Law of Thermodynamics—The Energy Equation 227 SOLUTION W • shaft = ? We include in our control volume the water contained in the pump between its entrance and exit sections. Application of Eq. 5.67 to the contents of this control volume on a time-average basis yields 0 (no elevation change) Control volume D 1 = 3.5 in. Pump D 2 = 1 in. Q = 300 gal/min. m # c ǔ 2 ǔ 1 a p b a p 2 b V 2 2 V 2 1 g1z 2 z 1 2d 1 2 0 (adiabatic flow) Q # W # net shaft (1) in net in We can solve directly for the power required by the pump, W # , from Eq. 1, after we first determine the mass flowrate, m # shaft net in , the speed of flow into the pump, V 1 , and the speed of the flow out of the pump, V 2 . All other quantities in Eq. 1 are given in the problem statement. From Eq. 5.6, we get m # rQ 11.94 slugs ft 3 21300 galmin2132.174 lbmslug2 17.48 galft 3 2160 smin2 41.8 lbms (2) Also from Eq. 5.6, so and V 1 Q 1300 gal/min24 112 in./ft2 2 A 1 17.48 gal/ft 3 2160 s/min2 13.5 in.2 2 10.0 ft/s V 2 Q 1300 gal/min24 112 in./ft22 A 2 17.48 gal/ft 3 2160 s/min2 11 in.2 2 123 ft/s V Q A Q D 2 /4 (3) (4) Section (1) p 1 = 18 psi F I G U R E E5.20 Substituting the values of Eqs. 2, 3, and 4 and values from the problem statement into Eq. 1 we obtain W # shaft net in u 2 – u 1 = 93 ft • ^ ^ lb/lbm Section (2) p 2 = 60 psi 141.8 lbms2c193 ftlblbm2 160 psi21144 in. 2 ft 2 2 11.94 slugsft 3 2132.174 lbmslug2 118 psi21144 in. 2 ft 2 2 11.94 slugsft 3 2132.174 lbmslug2 1123 ft s2 2 110.0 fts2 2 2332.174 1lbmft21lbs 2 24 d 1 32.2 hp 35501ftlb/s2/hp4 (Ans) COMMENT Of the total 32.2 hp, internal energy change accounts for 7.09 hp, the pressure rise accounts for 7.37 hp, and the kinetic energy increase accounts for 17.8 hp. E XAMPLE 5.21 Energy—Turbine Power per Unit Mass of Flow GIVEN A steam turbine generator unit used to produce electricity is shown in Fig. E5.21a. Assume the steam enters a turbine with a velocity of 30 m/s and enthalpy, ȟ 1 , of 3348 kJ/kg (see Fig. E5.21b). The steam leaves the turbine as a mixture of vapor and liquid having a velocity of 60 m/s and an enthalpy of 2550 kJ/kg. The flow through the turbine is adiabatic, and changes in elevation are negligible. FIND Determine the work output involved per unit mass of steam through-flow. F I G U R E E5.21a
- Page 200 and 201: 176 Chapter 4 ■ Fluid Kinematics
- Page 202 and 203: 178 Chapter 4 ■ Fluid Kinematics
- 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 252 and 253: 228 Chapter 5 ■ Finite Control Vo
- Page 254 and 255: 230 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
226 Chapter 5 ■ Finite Control Volume Analysis<br />
m • out<br />
m • in<br />
dA<br />
V<br />
Streamtube<br />
F I G U R E 5.7<br />
Streamtube flow.<br />
Furthermore, if there is only one stream entering and leaving the control volume, then<br />
aǔ p<br />
cs<br />
r V 2<br />
gzb rV nˆ dA <br />
2<br />
aǔ p r V 2<br />
2 gzb m # out aǔ p<br />
out<br />
r V 2<br />
2 gzb m # in<br />
in<br />
(5.66)<br />
Uniform flow as described above will occur in an infinitesimally small diameter streamtube as illustrated<br />
in Fig. 5.7. This kind of streamtube flow is representative of the steady flow of a particle<br />
of <strong>fluid</strong> along a pathline. We can also idealize actual conditions by disregarding nonuniformities<br />
in a finite cross section of flow. We call this one-dimensional flow and although such uniform flow<br />
rarely occurs in reality, the simplicity achieved with the one-dimensional approximation often justifies<br />
its use. More details about the effects of nonuniform distributions of velocities and other <strong>fluid</strong><br />
flow variables are considered in Section 5.3.4 and in Chapters 8, 9, and 10.<br />
If shaft work is involved, the flow must be unsteady, at least locally 1see Refs. 1 and 22. The<br />
flow in any <strong>fluid</strong> machine that involves shaft work is unsteady within that machine. For example,<br />
the velocity and pressure at a fixed location near the rotating blades of a fan are unsteady. However,<br />
upstream and downstream of the machine, the flow may be steady. Most often shaft work is<br />
associated with flow that is unsteady in a recurring or cyclical way. On a time-average basis for<br />
flow that is one-dimensional, cyclical, and involves only one stream of <strong>fluid</strong> entering and leaving<br />
the control volume, Eq. 5.64 can be simplified with the help of Eqs. 5.9 and 5.66 to form<br />
m # c ǔ out ǔ in a p r b a p<br />
out<br />
r b in<br />
V 2 out V 2 in<br />
2<br />
g1z out z in 2d Q # net<br />
in<br />
W # shaft<br />
net in<br />
(5.67)<br />
We call Eq. 5.67 the one-dimensional energy equation for steady-in-the-mean flow. Note that Eq. 5.67<br />
is valid for incompressible and compressible flows. Often, the <strong>fluid</strong> property called enthalpy, ȟ, where<br />
(5.68)<br />
ȟ ǔ p r<br />
The energy equation<br />
is sometimes<br />
written in terms of<br />
enthalpy.<br />
is used in Eq. 5.67. With enthalpy, the one-dimensional energy equation for steady-in-the-mean<br />
flow 1Eq. 5.672 is<br />
m # c ȟ out ȟ in V 2 out V 2 in<br />
2<br />
g1z out z in 2d Q # net<br />
in<br />
W # shaft<br />
net in<br />
(5.69)<br />
Equation 5.69 is often used for solving compressible flow problems. Examples 5.20 and 5.21<br />
illustrate how Eqs. 5.67 and 5.69 can be used.<br />
E XAMPLE 5.20<br />
Energy—Pump Power<br />
GIVEN A pump delivers water at a steady rate of 300 gal/min as<br />
shown in Fig. E5.20. Just upstream of the pump [section (1)]<br />
where the pipe diameter is 3.5 in., the pressure is 18 psi. Just<br />
downstream of the pump [section (2)] where the pipe diameter is<br />
1 in., the pressure is 60 psi. The change in water elevation across<br />
the pump is zero. The rise in internal energy of water, ǔ 2 ǔ 1 , associated<br />
with a temperature rise across the pump is 93 ft lb/lbm.<br />
The pumping process is considered to be adiabatic.<br />
FIND Determine the power (hp) required by the pump.