fluid_mechanics
240 Chapter 5 ■ Finite Control Volume Analysis z Semi-infinitesimal control volume θ x g θ d Flow F I G U R E 5.9 Semi-infinitesimal control volume. For all pure substances including common engineering working fluids, such as air, water, oil, and gasoline, the following relationship is valid 1see, for example, Ref. 32. T ds dǔ pd a 1 r b (5.92) where T is the absolute temperature and s is the entropy per unit mass. Combining Eqs. 5.91 and 5.92 we get m # c T ds pd a 1 r b d ap r b d aV2 or, dividing through by m # and letting dq net dQ # 2 b g dz d dQ# net netm # in , we obtain in dp 2 r d aV 2 b g dz 1T ds dq net2 in in (5.93) 5.4.2 Semi-infinitesimal Control Volume Statement of the Second Law of Thermodynamics A general statement of the second law of thermodynamics is D dQ # net in Dt sr dV a a sys T b sys (5.94) The second law of thermodynamics involves entropy, heat transfer, and temperature. or in words, the time rate of increase of the entropy of a system sum of the ratio of net heat transfer rate into system to absolute temperature for each particle of mass in the system receiving heat from surroundings The right-hand side of Eq. 5.94 is identical for the system and control volume at the instant when system and control volume are coincident; thus, a adQ# net in T b sys a a dQ# net in T b cv (5.95) With the help of the Reynolds transport theorem 1Eq. 4.192 the system time derivative can be expressed for the contents of the coincident control volume that is fixed and nondeforming. Using Eq. 4.19, we obtain D Dt sys sr dV 0 0t cv sr dV cs srV nˆ dA (5.96)
For a fixed, nondeforming control volume, Eqs. 5.94, 5.95, and 5.96 combine to give At any instant for steady flow 5.4 Second Law of Thermodynamics—Irreversible Flow 241 0 0t sr dV cs srV nˆ dA a a dQ# net in cv T 0 0t cv sr dV0 (5.97) (5.98) If the flow consists of only one stream through the control volume and if the properties are uniformly distributed 1one-dimensional flow2, Eqs. 5.97 and 5.98 lead to b cv m # dQ # net in 1s out s in 2 a T For the infinitesimally thin control volume of Fig. 5.8, Eq. 5.99 yields (5.99) m # dQ # net in ds a T (5.100) If all of the fluid in the infinitesimally thin control volume is considered as being at a uniform temperature, T, then from Eq. 5.100 we get The relationship between entropy and heat transfer rate depends on the process involved. or T ds dq net in T ds dq net in (5.101) The equality is for any reversible 1frictionless2 process; the inequality is for all irreversible 1friction2 processes. 0 5.4.3 Combination of the Equations of the First and Second Laws of Thermodynamics Combining Eqs. 5.93 and 5.101, we conclude that c dp r d aV2 2 b g dz d 0 (5.102) The equality is for any steady, reversible 1frictionless2 flow, an important example being flow for which the Bernoulli equation 1Eq. 3.7) is applicable. The inequality is for all steady, irreversible 1friction2 flows. The actual amount of the inequality has physical significance. It represents the extent of loss of useful or available energy which occurs because of irreversible flow phenomena including viscous effects. Thus, Eq. 5.102 can be expressed as c dp r d aV2 2 b g dz d d1loss2 1T ds dq net2 in (5.103) The irreversible flow loss is zero for a frictionless flow and greater than zero for a flow with frictional effects. Note that when the flow is frictionless, Eq. 5.103 multiplied by density, is identical to Eq. 3.5. Thus, for steady frictionless flow, Newton’s second law of motion 1see Section 3.12 and the first and second laws of thermodynamics lead to the same differential equation, dp r d aV2 r, (5.104) 2 b g dz 0
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240 Chapter 5 ■ Finite Control Volume Analysis<br />
z<br />
Semi-infinitesimal<br />
control volume<br />
<br />
θ<br />
x<br />
g<br />
θ<br />
d<br />
Flow<br />
F I G U R E 5.9<br />
Semi-infinitesimal control volume.<br />
For all pure substances including common engineering working <strong>fluid</strong>s, such as air, water, oil, and<br />
gasoline, the following relationship is valid 1see, for example, Ref. 32.<br />
T ds dǔ pd a 1 r b<br />
(5.92)<br />
where T is the absolute temperature and s is the entropy per unit mass.<br />
Combining Eqs. 5.91 and 5.92 we get<br />
m # c T ds pd a 1 r b d ap r b d aV2<br />
or, dividing through by m # and letting dq net dQ # 2 b g dz d dQ# net<br />
netm # in<br />
, we obtain<br />
in<br />
dp<br />
2<br />
r d aV 2 b g dz 1T ds dq net2<br />
in<br />
in<br />
(5.93)<br />
5.4.2 Semi-infinitesimal Control Volume Statement<br />
of the Second Law of Thermodynamics<br />
A general statement of the second law of thermodynamics is<br />
D<br />
dQ # net<br />
in<br />
Dt sr dV a a<br />
sys T<br />
b sys<br />
(5.94)<br />
The second law of<br />
thermodynamics involves<br />
entropy, heat<br />
transfer, and temperature.<br />
or in words,<br />
the time rate of increase of the<br />
entropy of a system<br />
sum of the ratio of net heat<br />
transfer rate into system to<br />
absolute temperature for each<br />
particle of mass in the system<br />
receiving heat from<br />
surroundings<br />
The right-hand side of Eq. 5.94 is identical for the system and control volume at the instant when<br />
system and control volume are coincident; thus,<br />
a adQ# net<br />
in<br />
T<br />
b sys<br />
a a dQ# net<br />
in<br />
T<br />
b cv<br />
(5.95)<br />
With the help of the Reynolds transport theorem 1Eq. 4.192 the system time derivative can be expressed<br />
for the contents of the coincident control volume that is fixed and nondeforming. Using<br />
Eq. 4.19, we obtain<br />
D<br />
Dt sys<br />
sr dV 0 0t cv<br />
sr dV cs<br />
srV nˆ dA<br />
(5.96)