fluid_mechanics
170 Chapter 4 ■ Fluid Kinematics If we combine Eqs. 4.10, 4.11, 4.12, and 4.13 we see that the relationship between the time rate of change of B for the system and that for the control volume is given by or DB sys Dt 0B cv dt B # out B # in (4.14) The time derivative associated with a system may be different from that for a control volume. DB sys Dt 0B cv 0t r 2 A 2 V 2 b 2 r 1 A 1 V 1 b 1 (4.15) This is a version of the Reynolds transport theorem valid under the restrictive assumptions associated with the flow shown in Fig. 4.11—fixed control volume with one inlet and one outlet having uniform properties 1density, velocity, and the parameter b2 across the inlet and outlet with the velocity normal to sections 112 and 122. Note that the time rate of change of B for the system 1the left-hand side of Eq. 4.15 or the quantity in Eq. 4.82 is not necessarily the same as the rate of change of B within the control volume 1the first term on the right-hand side of Eq. 4.15 or the quantity in Eq. 4.92. This is true because the inflow rate 1b 1 r 1 V 1 A 1 2 and the outflow rate 1b 2 r 2 V 2 A 2 2 of the property B for the control volume need not be the same. E XAMPLE 4.8 Use of the Reynolds Transport Theorem GIVEN Consider again the flow from the fire extinguisher shown in Fig. E4.7. Let the extensive property of interest be the system mass 1B m, the system mass, or b 12. FIND Write the appropriate form of the Reynolds transport theorem for this flow. SOLUTION Again we take the control volume to be the fire extinguisher, and the system to be the fluid within it at time t 0. For this case there is no inlet, section 112, across which the fluid flows into the control volume 1A 1 02. There is, however, an outlet, section 122. Thus, the Reynolds transport theorem, Eq. 4.15, along with Eq. 4.9 with b 1 can be written as 0 a Dm sys r dVb cv r (1) (Ans) Dt 0t 2 A 2 V 2 COMMENT If we proceed one step further and use the basic law of conservation of mass, we may set the left-hand side of this equation equal to zero 1the amount of mass in a system is constant2 and rewrite Eq. 1 in the form 0 a cv r dVb r 0t 2 A 2 V 2 (2) The physical interpretation of this result is that the rate at which the mass in the tank decreases in time is equal in magnitude but opposite to the rate of flow of mass from the exit, r 2 A 2 V 2 . Note the units for the two terms of Eq. 2 1kgs or slugss2. Note that if there were both an inlet and an outlet to the control volume shown in Fig. E4.7, Eq. 2 would become 0 a r dVb cv r (3) 0t 1 A 1 V 1 r 2 A 2 V 2 In addition, if the flow were steady, the left-hand side of Eq. 3 would be zero 1the amount of mass in the control would be constant in time2 and Eq. 3 would become r 1 A 1 V 1 r 2 A 2 V 2 This is one form of the conservation of mass principle discussed in Sect. 3.6.2—the mass flowrates into and out of the control volume are equal. Other more general forms are discussed in Chapter 5. Right Atrium Left Atrium Right Ventricle Left Ventricle Equation 4.15 is a simplified version of the Reynolds transport theorem. We will now derive it for much more general conditions. A general, fixed control volume with fluid flowing through it is shown in Fig. 4.12. The flow field may be quite simple 1as in the above one-dimensional flow considerations2, or it may involve a quite complex, unsteady, three-dimensional situation such as the flow through a human heart as illustrated by the figure in the margin. In any case we again consider the system to be the fluid within the control volume at the initial time t. A short time later a portion of the fluid 1region II2 has exited from the control volume and additional fluid 1region I, not part of the original system2 has entered the control volume.
4.4 The Reynolds Transport Theorem 171 Inflow CV–I II V 2 II c V 3 I b II b II a I a II d V 5 V 1 V 6 V 4 I Outflow Fixed control surface and system boundary at time t System boundary at time t + δ t F I G U R E 4.12 Control volume and system for flow through an arbitrary, fixed control volume. F I G U R E 4.13 inlet and outlet. Typical control volume with more than one The simplified Reynolds transport theorem can be easily generalized. We consider an extensive fluid property B and seek to determine how the rate of change of B associated with the system is related to the rate of change of B within the control volume at any instant. By repeating the exact steps that we did for the simplified control volume shown in Fig. 4.11, we see that Eq. 4.14 is valid for the general case also, provided that we give the correct interpretation to the terms B # and B # out in. In general, the control volume may contain more 1or less2 than one inlet and one outlet. A typical pipe system may contain several inlets and outlets as are shown in Fig. 4.13. In such instances we think of all inlets grouped together and all outlets grouped together at least conceptually. The term B # 1II II a II b II c p 1I I a I b I c p 2 2, out represents the net flowrate of the property B from the control volume. Its value can be thought of as arising from the addition 1integration2 of the contributions through each infinitesimal area element of size dA on the portion of the control surface dividing region II and the control volume. This surface is denoted CS out . As is indicated in Fig. 4.14, in time dt the volume of fluid that passes across each area element is given by dV d/ n dA, where d/ n d/ cos u is the height 1normal to the base, dA2 of the small volume element, and u is the angle between the velocity vector and the outward pointing normal to the surface, nˆ . Thus, since d/ V dt, the amount of the property B carried across the area element dA in the time interval dt is given by dB br dV br1V cos u dt2 dA The rate at which B is carried out of the control volume across the small area element denoted dB # dA, out, is dB # rb dV 1rbV cos u dt2 dA out lim lim rbV cos u dA dtS0 dt dtS0 dt CS out Outflow portion of control surface ^ n δV = δ n δA n^ δ n ^ n δA θ δA θ θ V δ = V δt V δ V (a) (b) (c) F I G U R E 4.14 Outflow across a typical portion of the control surface.
- Page 144 and 145: 120 Chapter 3 ■ Elementary Fluid
- Page 146 and 147: 122 Chapter 3 ■ Elementary Fluid
- Page 148 and 149: 124 Chapter 3 ■ Elementary Fluid
- Page 150 and 151: 126 Chapter 3 ■ Elementary Fluid
- Page 152 and 153: 128 Chapter 3 ■ Elementary Fluid
- Page 154 and 155: 130 Chapter 3 ■ Elementary Fluid
- Page 156 and 157: 132 Chapter 3 ■ Elementary Fluid
- Page 158 and 159: 134 Chapter 3 ■ Elementary Fluid
- Page 160 and 161: 136 Chapter 3 ■ Elementary Fluid
- Page 162 and 163: 138 Chapter 3 ■ Elementary Fluid
- Page 164 and 165: 140 Chapter 3 ■ Elementary Fluid
- Page 166 and 167: 142 Chapter 3 ■ Elementary Fluid
- Page 168 and 169: 144 Chapter 3 ■ Elementary Fluid
- Page 170 and 171: 146 Chapter 3 ■ Elementary Fluid
- Page 172 and 173: 148 Chapter 4 ■ Fluid Kinematics
- Page 174 and 175: 150 Chapter 4 ■ Fluid Kinematics
- Page 176 and 177: 152 Chapter 4 ■ Fluid Kinematics
- Page 178 and 179: 154 Chapter 4 ■ Fluid Kinematics
- Page 180 and 181: 156 Chapter 4 ■ Fluid Kinematics
- Page 182 and 183: 158 Chapter 4 ■ Fluid Kinematics
- Page 184 and 185: 160 Chapter 4 ■ Fluid Kinematics
- Page 186 and 187: 162 Chapter 4 ■ Fluid Kinematics
- Page 188 and 189: 164 Chapter 4 ■ Fluid Kinematics
- Page 190 and 191: 166 Chapter 4 ■ Fluid Kinematics
- Page 192 and 193: 168 Chapter 4 ■ Fluid Kinematics
- Page 196 and 197: 172 Chapter 4 ■ Fluid Kinematics
- Page 198 and 199: 174 Chapter 4 ■ Fluid Kinematics
- 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
4.4 The Reynolds Transport Theorem 171<br />
Inflow<br />
CV–I<br />
II<br />
V 2<br />
II c<br />
V 3<br />
I b<br />
II b<br />
II a<br />
I a II d<br />
V 5<br />
V 1<br />
V 6<br />
V 4<br />
I<br />
Outflow<br />
Fixed control surface and system<br />
boundary at time t<br />
System boundary at time t + δ t<br />
F I G U R E 4.12 Control volume<br />
and system for flow through an arbitrary, fixed<br />
control volume.<br />
F I G U R E 4.13<br />
inlet and outlet.<br />
Typical control volume with more than one<br />
The simplified<br />
Reynolds transport<br />
theorem can be<br />
easily generalized.<br />
We consider an extensive <strong>fluid</strong> property B and seek to determine how the rate of change of B<br />
associated with the system is related to the rate of change of B within the control volume at any<br />
instant. By repeating the exact steps that we did for the simplified control volume shown in Fig.<br />
4.11, we see that Eq. 4.14 is valid for the general case also, provided that we give the correct<br />
interpretation to the terms B # and B # out in. In general, the control volume may contain more 1or less2<br />
than one inlet and one outlet. A typical pipe system may contain several inlets and outlets as are<br />
shown in Fig. 4.13. In such instances we think of all inlets grouped together<br />
and all outlets grouped together<br />
at least conceptually.<br />
The term B # 1II II a II b II c p 1I I a I b I c p 2<br />
2,<br />
out represents the net flowrate of the property B from the control volume. Its<br />
value can be thought of as arising from the addition 1integration2 of the contributions through<br />
each infinitesimal area element of size dA on the portion of the control surface dividing region<br />
II and the control volume. This surface is denoted CS out . As is indicated in Fig. 4.14, in time dt<br />
the volume of <strong>fluid</strong> that passes across each area element is given by dV d/ n dA, where<br />
d/ n d/ cos u is the height 1normal to the base, dA2 of the small volume element, and u is the<br />
angle between the velocity vector and the outward pointing normal to the surface, nˆ . Thus,<br />
since d/ V dt, the amount of the property B carried across the area element dA in the time<br />
interval dt is given by<br />
dB br dV br1V cos u dt2 dA<br />
The rate at which B is carried out of the control volume across the small area element denoted<br />
dB # dA,<br />
out, is<br />
dB # rb dV 1rbV cos u dt2 dA<br />
out lim lim<br />
rbV cos u dA<br />
dtS0 dt dtS0 dt<br />
CS out<br />
Outflow<br />
portion of<br />
control<br />
surface<br />
^<br />
n<br />
δV = δ n δA<br />
n^<br />
δ n<br />
^<br />
n<br />
δA<br />
θ<br />
δA<br />
θ<br />
θ<br />
V<br />
δ = V δt<br />
V<br />
δ<br />
V<br />
(a) (b) (c)<br />
F I G U R E 4.14 Outflow across a typical portion of the control surface.