Modern Engineering Thermodynamics

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efficiency increase if the condenser pressure is lowered from 0.100 to 1.00 × 10 –3 MPa? 24. Steam enters the turbine of a Rankine cycle power plant at 200. psia and 500.°F. How much does the isentropic thermal efficiency increase if the condenser pressure is lowered from 14.7 to 1.00 psia? 25. Steam leaves the boiler of a Rankine cycle power plant at 3000. psia and 1000.°F. It is isenthalpically throttled to 600. psia before it enters the turbine. It then exits the turbine at 1.00 psia. Neglecting the pump work, determine a. The maximum thermal efficiency of this plant. b. Its maximum thermal efficiency if the boiler is operated at 600. psia and 1000.°F and no throttling occurs at the entrance to the turbine. 26. Steam exits a boiler and enters a turbine at 200. psia, 600.°F with a mass flow rate of 30.0 × 10 3 lbm/h. It exits the turbine at 1.00 psia and is condensed. The condensate then reenters the boiler as a saturated liquid at 90.0°F. The turbine drives an electrical generator that delivers a net 3000. kW of power. Determine a. The Rankine cycle actual thermal efficiency of the entire system. b. The isentropic efficiency of the combined turbine–generator unit. 27. An isentropic Rankine cycle using steam is shown in Figure 13.68. For the given data, determine a. The quality of the turbine exhaust steam. b. The cycle thermal efficiency. c. The mass flow rate required to produce 10,000 Btu/s net output power. W P FIGURE 13.68 Problem 27. p 2 = 3:00 psia p 3 = 3:00 psia p 4 = 1000: psia s at 1.00 MPa. 2 = s 1 x 3 = 0:00 s 4 = s 3 35. Steam at 600. psia and 800.°F enters the high-pressure stage of Problems 529 1.00 to 20.0 MPa. Ignore the power required by the boiler feed pump. 29.* Steam is supplied to a turbine at a rate of 1.00 × 10 6 kg/h at 500.°C and 10.0 MPa, and it exhausts to a condenser at 2.00 kPa. A single open loop regenerator is used to heat the boiler feedwater with steam extracted from the turbine at 6.00 MPa. The condensate exits the regenerator at 6.00 MPa as a saturated liquid. Neglecting the pump power, determine a. The mass flow rate of steam extracted from the turbine. b. The system’s isentropic Rankine cycle thermal efficiency. c. The isentropic Rankine cycle thermal efficiency of the same system without a regenerator. d. The percent increase in thermal efficiency due to the regenerator. 30. Steam enters a turbine with an isentropic efficiency of 83.0% at 300. psia, 800.°F and exhausts to a condenser at 0.250 psia. The boiler feedwater is heated in a single, open loop regenerator with steam extracted from the turbine at 100. psia. Saturated liquid leaves the regenerator at the pressure of the extraction steam. Neglecting all pump work, determine a. The percent mass flow of steam extracted from the turbine. b. The turbine power output per unit mass flow of steam. c. The system thermal efficiency. d. The turbine power output per unit mass flow of steam when the regenerator is not in use. e. The system thermal efficiency when the regenerator is not in use. f. The percent increase in system thermal efficiency produced by the regenerator. 31. Repeat items a, b, and c of Problem 30 for steam extraction pressures of 75.0, 50.0, 25.0, and 10.0 psia and plot these Q H results vs. the extraction pressure. 32. A turbine having an isentropic efficiency of 86.0% receives steam at 4.00 × 10 6 lbm/h, 300. psia, 1000.°F and exhausts it to 4 1 a condenser at 1.00 psia. Steam is extracted from the turbine at Boiler 788,000 lbm/h and 200. psia to heat the boiler feedwater in a single, closed loop regenerator. The extract steam then exits the Pump Turbine W regenerator as a saturated liquid. Neglecting the pump power, T determine a. The pressure and temperature of the extract steam as it leaves 3 Condenser the regenerator. 2 b. The Rankine cycle thermal efficiency of this system. Q L c. The Rankine cycle thermal efficiency of this system without regeneration. d. The percent increase in thermal efficiency due to the regenerator. 33. Determine the blade tip velocity of DeLaval’s first steam turbine. It had a rotor diameter of 3.00 inches and ran at 40.0 × 10 3 rpm. 34.* Determine the isentropic exit velocity from a reaction turbine nozzle if steam enters the nozzle at 30.0 MPa, 500.°C and exits an isentropic turbine and is reheated to 60.0 psia and 700.°F before entering the low-pressure stage. The steam then exhausts to a condenser at 1.00 psia. Neglecting pump power, determine a. The isentropic Rankine cycle thermal efficiency. b. The isentropic Rankine cycle thermal efficiency that would occur if the steam were not reheated. c. The percent increase in thermal efficiency due to the reheating operation. Station 1 Station 2 Station 3 Station 4 p 1 = 1000: psia T 1 = 1000:°F The process path from station 1 to 2 is an isentropic expansion and that from station 3 to 4 is an isentropic compression. 28.* For a constant steam boiler temperature of 400.°C, a constant turbine exhaust moisture content of 5.00%, and a constant condenser pressure of 3.00 kPa, plot the Rankine cycle thermal efficiency vs. boiler pressure over the boiler pressure range from
530 CHAPTER 13: Vapor and Gas Power Cycles 36. Steam enters the high-pressure turbine of a Rankine cycle power plant at 1200. psia and 700.°F and exits as a saturated vapor. It is then reheated to 600.°F before it enters the low-pressure turbine, which exhausts to a condenser at 1.00 psia. The isentropic efficiencies of the high- and low-pressure turbines and the boiler feed pump are 88.0%, 79.0%, and 65.0%, respectively. Determine the thermal efficiency and the net power per unit mass flow rate of steam for this plant. 37.* Consider a steam turbine with a constant inlet temperature of 500.°C connected to a constant pressure condenser at 1.00 kPa. When the steam expands to a saturated vapor in the turbine, it is removed and reheated in the boiler to 500.°C then returned to the turbine to continue to expand until it reaches the condenser pressure. The turbine isentropic efficiency is constant at 80.0%. Ignoring the boiler feed pump power, plot a. The Rankine cycle thermal efficiency. b. The percent moisture in the turbine exhaust vs. the boiler pressure over a boiler pressure range of 1.00 to 20.0 MPa. Computerized steam tables are recommended for this problem. 38. The first steam turbine used in an American electrical power plant was a Westinghouse reaction turbine of the Parson’s type installed at the Hartford, Connecticut, Electric Light Company in 1902. The turbine inlet state was 200. psig and 400.°F, the generator produced 2.00 MW, and the plant had a heat rate of 35.0 × 10 3 Btu/(kW · h). Determine its thermal efficiency. 39. In 1903, a General Electric Curtis impulse steam turbine was installed at the Fisk Street Station of the Commonwealth Electric Company in Chicago, Illinois, and was at that time the most powerful steam turbine in the world. 13 The turbine inlet state was 175 psig with 150.°F of superheat, and the condenser pressure was 1.50 in of mercury. When the generator produced a net 5000. kW, the steam flow rate per unit of electrical power produced ( _m / _W elect: ) was 22.5 lbm/(kW · h). For this unit, determine a. The isentropic power output of the turbine. b. The isentropic efficiency of the turbine-generator unit. c. The isentropic Rankine cycle thermal efficiency of the power plant, assuming saturated liquid exits the condenser and neglecting pump work. 40. In 1939, the Port Washington, Wisconsin, power plant of the Milwaukee Electric Railway and Light Company 14 had an unusually high heat rate of 10,800 Btu/(kW · h). Determine its thermal efficiency. 41. Refrigerant-22 is used as the working fluid in a 1.00 MW Rankine bottoming cycle for a steam power plant. The bottoming cycle turbine inlet state is saturated vapor at 210.°F, and the condenser outlet is saturated liquid at 70.0°F. The turbine and pump isentropic efficiencies are 85.0% and 70.0%, respectively. Determine a. The thermal efficiency of the bottoming cycle. b. The ratio of the pump to turbine power. c. The required mass flow rate of refrigerant. 42. It is common to model hot ASC performance with the same formula used in cold ASC analysis except that a specific heat ratio (k) typical of high-temperature gas is used. Determine the Carnot ASC thermal efficiency of an engine with an 8.00 to 1 compression ratio, using a. A cold ASC analysis with k = 1.40. b. A hot ASC analysis with k = 1.30. c. Determine the percent decrease in the Carnot thermal efficiency between the cold and hot ASC analysis. 43. Air enters an engine at 40.0°F and is compressed isentropically in a 9.00 to 1 compression ratio. Determine the Carnot ASC thermal efficiency of this engine, using a. A cold ASC analysis with k = 1.40. b. A hot ASC analysis using the gas tables (Table C.16a in Thermodynamic Tables to accompany Modern Engineering Thermodynamics). c. Determine the percent decrease in the Carnot thermal efficiency between the cold and hot ASC analysis. 44.* Air enters an engine at atmospheric pressure and 17.0°C and is isentropically compressed to 871.4 kPa. Determine the Carnot ASC thermal efficiency of the engine, using a. A cold ASC analysis with k = 1.40. b. A hot ASC analysis using the gas tables (Table C.16b). c. Determine the percent decrease in the Carnot thermal efficiency between the cold and hot ASC analysis. 45. Determine the mechanical efficiency of a Stirling cycle engine operating with a 1300.°F heater and a 100.°F cooler. The engine produces a net 10.0 hp output with a heat input of 80.0 × 10 3 Btu/h. 46. In 1964, an experimental Stirling engine was installed in a modified Chevrolet Corvair at the General Motors Research Laboratory. Alumina (aluminum oxide) heated to 1200.°F served as the heat source for the engine, while the atmosphere at 100.°F served as the heat sink (because of the use of alumina in the engine, the car was dubbed the Calvair by GM researchers). Assuming a mechanical efficiency of 67.0%, determine the actual thermal efficiency of the engine based on a cold ASC analysis. 47. A Stirling cycle engine uses 0.0800 lbm of air as the working fluid. Heat is added to this air isothermally at 1500.°F and is rejected isothermally at 200.°F. The initial volume of the air before the heat addition (V 4 in Figure 13.38) is 0.750 ft 3 and the final volume after the heat addition (V 1 in Figure 13.38) is 1.00 ft 3 . For the cold ASC, determine a. The air pressure at the beginning and end of the expansion stroke (p 4 and p 1 in Figure 13.38). b. The air pressure at the beginning and end of the compression stroke (p 2 and p 3 in Figure 13.38). c. The cold ASC thermal efficiency of the engine. d. The net reversible work produced inside the engine per cycle of operation. 48. In 1853, John Ericsson constructed a huge 300. hp hot air engine that ran on the Ericsson cycle. It had pistons 14.0 ft in diameter and it consumed 2.00 lbm of coal per indicated 13 On May 28, 1975, this turbine-generator unit was designated as the seventh National Historic Mechanical Engineering Landmark by the American Society of Mechanical engineers. 14 In 1980, this power plant was designated as the 48th National Historic Mechanical Engineering Landmark by the American Society of Mechanical Engineers.
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Modern Engineering Thermodynamics
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Modern Engineering Thermodynamics R
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Dedication WHAT IS AN ENGINEER AND
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Contents PREFACE . . . . . . . . .
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Contents ix 7.6 Heat Engines Runnin
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Contents xi 14.13 Air Standard Gas
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Preface TEXT OBJECTIVES This textbo
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Preface xv Step 5. Write down the b
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Acknowledgments I wish to acknowled
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Resources That Accompany This Book
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List of Symbols A a B COP CR c c p
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Prologue PARIS FRANCE, 10:35 AM, AU
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CHAPTER 1 The Beginning CONTENTS 1.
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1.2 Why Is Thermodynamics Important
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1.3 Getting Answers: A Basic Proble
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1.5 How Do We Measure Things? 7 bei
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1.6 Temperature Units 9 THE DEVELOP
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1.7 Classical Mechanical and Electr
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1.7 Classical Mechanical and Electr
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1.9 Modern Units Systems 15 where M
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1.10 Significant Figures 17 CRITICA
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1.10 Significant Figures 19 WHAT AB
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1.11 Potential and Kinetic Energies
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1.11 Potential and Kinetic Energies
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Summary 25 FIGURE 1.19 Case study 1
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Problems 27 Problems (* indicates p
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Problems 29 14. Determine the mass
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Problems 31 49. Using the CGS units
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CHAPTER 2 Thermodynamic Concepts CO
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2.3 Phases of Matter 35 System boun
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2.4 System States and Thermodynamic
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2.6 Thermodynamic Processes 39 WHAT
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2.7 Pressure and Temperature Scales
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2.9 The Continuum Hypothesis 43 Sur
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2.10 The Balance Concept 45 Solutio
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2.11 The Conservation Concept 47 or
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2.11 The Conservation Concept 49 Th
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Summary 51 change in the mass of X
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Problems 53 Problems (* indicates p
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Problems 55 and Death rate = α 2 +
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CHAPTER 3 Thermodynamic Properties
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3.3 Fun with Mathematics 59 CRITICA
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3.4 Some Exciting New Thermodynamic
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3.6 Enthalpy 63 WHO WAS AMALIE EMMY
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3.7 Phase Diagrams 65 WHO WAS EMMY
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Pressure Vapor 3.7 Phase Diagrams 6
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3.7 Phase Diagrams 69 WHAT IS A “
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3.7 Phase Diagrams 71 considerable
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3.8 Quality 73 10 5 300 C Critical
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3.8 Quality 75 Although Eq. (3.26)
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3.9 Thermodynamic Equations of Stat
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3.10 Thermodynamic Tables 85 Critic
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3.12 Thermodynamic Charts 87 vð100
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3.13 Thermodynamic Property Softwar
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Summary 91 and e = E/m = u + V2 2g
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Problems 93 c. For a saturated mixt
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Problems 95 specific enthalpy of sa
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Problems 97 Table 3.23 Problem 65 M
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CHAPTER 4 The First Law of Thermody
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4.3 The First Law of Thermodynamics
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4.3 The First Law of Thermodynamics
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4.4 Energy Transport Mechanisms 105
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4.5 Point and Path Functions 107 4.
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4.6 Mechanical Work Modes of Energy
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4.7 Nonmechanical Work Modes of Ene
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4.9 Work Efficiency 125 In the case
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4.12 Heat Modes of Energy Transport
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4.13 Heat Transfer Modes 129 Table
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4.14 A Thermodynamic Problem Solvin
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4.14 A Thermodynamic Problem Solvin
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4.15 How to Write a Thermodynamics
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4.15 How to Write a Thermodynamics
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Summary 139 The general open system
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Problems 141 11.* Determine the hea
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Problems 143 where K = 0.810 lbf. D
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Problems 145 Table 4.12 Problem 67
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CHAPTER 5 First Law Closed System A
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5.2 Sealed, Rigid Containers 149 In
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5.4 Power Plants 151 Step 7. Calcul
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5.5 Incompressible Liquids 153 The
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1Q 2 − 1 W 2 = mðu 2 − u 1 Þ
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5.8 Closed System Unsteady State Pr
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5.9 The Explosive Energy of Pressur
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Problems 161 Problems (* indicates
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Problems 163 31. A thermoelectric g
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Problems 165 where v, T, and r are
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CHAPTER 6 First Law Open System App
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6.2 Mass Flow Energy Transport 169
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6.3 Conservation of Energy and Cons
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6.4 Flow Stream Specific Kinetic an
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6.5 Nozzles and Diffusers 175 m (a)
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6.5 Nozzles and Diffusers 177 We ar
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6.6 Throttling Devices 179 These as
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6.6 Throttling Devices 181 For an i
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6.7 Throttling Calorimeter 183 The
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6.8 Heat Exchangers 185 Convective
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6.9 Shaft Work Machines 187 6.9 SHA
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6.9 Shaft Work Machines 189 1 Basem
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6.10 Open System Unsteady State Pro
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Problems 197 we have _m R / _m D =
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Problems 201 32.* A commercial slid
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Summary 203 59. Incompressible liqu
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CHAPTER 7 Second Law of Thermodynam
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7.3 The Second Law of Thermodynamic
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7.4 Carnot’s Heat Engine and the
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7.4 Carnot’s Heat Engine and the
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7.5 The Absolute Temperature Scale
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7.5 The Absolute Temperature Scale
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7.6 Heat Engines Running Backward 2
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7.7 Clausius’s Definition of Entr
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7.8 Numerical Values for Entropy 22
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7.10 Differential Entropy Balance 2
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7.11 Heat Transport of Entropy 229
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7.13 Entropy Production Mechanisms
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7.14 Heat Transfer Production of En
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7.15 Work Mode Production of Entrop
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7.15 Work Mode Production of Entrop
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7.16 Phase Change Entropy Productio
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Summary 241 ■ Indirect method inv
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Problems 243 amount of work W irr i
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Problems 245 a. If the heat pump is
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Problems 247 51. Develop a program
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CHAPTER 8 Second Law Closed System
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8.2 Systems Undergoing Reversible P
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8.3 Systems Undergoing Irreversible
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8.4 Diffusional Mixing 271 Exercise
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Summary 273 Note that this example
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Problems 275 15. A 20.0 ft 3 tank c
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Problems 277 46. a. Determine a for
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CHAPTER 9 Second Law Open System Ap
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9.4 Open System Entropy Balance Equ
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9.4 Open System Entropy Balance Equ
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9.5 Nozzles, Diffusers, and Throttl
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9.5 Nozzles, Diffusers, and Throttl
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9.6 Heat Exchangers 289 Exercises 1
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9.6 Heat Exchangers 291 (T H ) (T H
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9.7 Mixing 293 Now, _m air is given
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9.7 Mixing 295 Critical value of y,
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9.9 Unsteady State Processes in Ope
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Problems 309 Multiplying this equat
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Problems 311 entropy production rat
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Problems 313 heat is added to the b
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Problems 315 55.* Determine the max
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Problems 317 The cavitation process
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CHAPTER 10 Availability Analysis CO
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10.3 What Are Conservative Forces?
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10.6 Availability 323 WHAT IS A SYS
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10.6 Availability 325 and the total
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10.7 Closed System Availability Bal
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10.7 Closed System Availability Bal
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10.8 Flow Availability 331 EXAMPLE
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s − s 0 = c ln T T 0 10.8 Flow Av
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10.10 Modified Availability Rate Ba
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10.10 Modified Availability Rate Ba
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10.11 Energy Efficiency Based on th
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Summary 351 In this problem, we hav
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Summary 353 7. The general open sys
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Problems 355 12.5 Btu/hr·ft ·R. I
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Problems 357 flow rate of 15.0 lbm/
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Problems 359 85. Create a specific
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CHAPTER 11 More Thermodynamic Relat
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11.2 Two New Properties: Helmholtz
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11.2 Two New Properties: Helmholtz
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11.4 Maxwell Equations 367 11.4 MAX
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11.4 Maxwell Equations 369 then,
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11.5 The Clapeyron Equation 371 and
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11.6 Determining u, h, and s from p
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11.7 Constructing Tables and Charts
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11.8 Thermodynamic Charts 381 so th
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11.9 Gas Tables 383 where p r is th
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11.10 Compressibility Factor and Ge
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11.11 Is Steam Ever an Ideal Gas? 3
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Summary 399 equation, and a series
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Problems 401 20.* Estimate h fg for
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Problems 403 Design Problems The fo
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CHAPTER 12 Mixtures of Gases and Va
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12.2 Thermodynamic Properties of Ga
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12.3 Mixtures of Ideal Gases 413 Th
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12.3 Mixtures of Ideal Gases 415 Co
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12.4 Psychrometrics 417 Finally, th
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12.4 Psychrometrics 419 EXAMPLE 12.
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12.6 The Sling Psychrometer 421 The
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12.6 The Sling Psychrometer 423 p w
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12.7 Air Conditioning 425 WHAT ENVI
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12.8 Psychrometric Enthalpies 427 E
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12.8 Psychrometric Enthalpies 429 o
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12.9 Mixtures of Real Gases 431 Whe
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12.9 Mixtures of Real Gases 433 and
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12.9 Mixtures of Real Gases 435 The
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12.9 Mixtures of Real Gases 437 Sol
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Summary 439 Last, we combine Dalton
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Problems 443 exhaust gas is an idea
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Problems 445 57.* Cooling towers ar
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CHAPTER 13 Vapor and Gas Power Cycl
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13.2 Part I. Engines and Vapor Powe
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13.4 Rankine Cycle 457 A B Reversib
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13.5 Operating Efficiencies 459 For
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13.5 Operating Efficiencies 461 13.
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13.5 Operating Efficiencies 463 b.
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13.5 Operating Efficiencies 465 Sta
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13.6 Rankine Cycle with Superheat 4
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13.7 Rankine Cycle with Regeneratio
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13.8 The Development of the Steam T
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13.9 Rankine Cycle with Reheat 477
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Page 518 and 519: 13.15 Lenoir Cycle 493 Exercises 28
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Page 524 and 525: 13.17 Aircraft Gas Turbine Engines
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Page 550 and 551: Summary 525 Fill port 160 mm End of
Page 552 and 553: Problems 527 7. The thermal efficie
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14.18 Second Law Analysis of Refrig
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14.18 Second Law Analysis of Refrig
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2. The coefficient of performance o
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Problems 585 13.* A refrigeration u
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Problems 587 Loop B Station 1B Stat
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Problems 589 under these conditions
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CHAPTER 15 Chemical Thermodynamics
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15.2 Stoichiometric Equations 593 1
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15.2 Stoichiometric Equations 595 C
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15.3 Organic Fuels 597 ANSWERS SOME
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15.4 Fuel Modeling 599 Hydrocarbon
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15.4 Fuel Modeling 601 equation, si
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15.5 Standard Reference State 603 I
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15.6 Heat of Formation 605 and H 2
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15.7 Heat of Reaction 607 EXAMPLE 1
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15.7 Heat of Reaction 609 CRITICAL
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15.7 Heat of Reaction 611 Then, h P
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15.8 Adiabatic Flame Temperature 61
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15.9 Maximum Explosion Pressure 619
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15.10 Entropy Production in Chemica
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15.10 Entropy Production in Chemica
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15.11 Entropy of Formation and Gibb
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15.12 Chemical Equilibrium and Diss
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H 2 O !ð1 − yÞH 2 O + yðv H2
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15.14 The van’t Hoff Equation 635
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15.15 Fuel Cells 637 Anode Electrol
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15.15 Fuel Cells 639 The maximum po
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15.16 Chemical Availability 641 and
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ðn i /n fuel Þðc pi Þ E system
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Problems 645 where j = 4n + m kgmol
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Problems 647 c. The percent excess
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Problems 649 77. Determine the mola
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CHAPTER 16 Compressible Fluid Flow
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16.3 Isentropic Stagnation Properti
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16.4 The Mach Number 655 Note that
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16.4 The Mach Number 657 Table 16.1
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16.4 The Mach Number 659 Since for
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16.5 Converging-Diverging Flows 661
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16.5 Converging-Diverging Flows 663
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16.6 Choked Flow 665 T a a p a = co
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16.6 Choked Flow 667 Exercises 16.
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16.7 Reynolds Transport Theorem 669
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16.7 Reynolds Transport Theorem 671
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16.8 Linear Momentum Rate Balance 6
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16.9 Shock Waves 675 16.9 SHOCK WAV
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16.9 Shock Waves 677 and, for an id
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16.9 Shock Waves 679 6 5 4 S P /(m
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16.10 Nozzle and Diffuser Efficienc
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16.10 Nozzle and Diffuser Efficienc
Page 710 and 711:
Summary 685 Since for a diffuser, M
Page 712 and 713:
Page 714 and 715:
43. 0.800 lbm/s of air passes throu
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Problems 691 A plot of this functio
Page 718 and 719:
CHAPTER 17 Thermodynamics of Biolog
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17.3 Thermodynamics of Biological C
Page 722 and 723:
17.3 Thermodynamics of Biological C
Page 724 and 725:
17.4 Energy Conversion Efficiency o
Page 726 and 727:
17.4 Energy Conversion Efficiency o
Page 728 and 729:
17.5 Metabolism 703 Table 17.3 Brea
Page 730 and 731:
17.6 Thermodynamics of Nutrition an
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Page 734 and 735:
Page 736 and 737:
17.7 Limits to Biological Growth 71
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17.7 Limits to Biological Growth 71
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17.8 Locomotion Transport Number 71
Page 742 and 743:
17.9 Thermodynamics of Aging and De
Page 744 and 745:
17.9 Thermodynamics of Aging and De
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1/3 V most efficient = P o ρAC D S
Page 748 and 749:
Problems 723 a. If the monster cons
Page 750 and 751:
Problems 725 the officer asks Paul
Page 752 and 753:
CHAPTER 18 Introduction to Statisti
Page 754 and 755:
18.3 Kinetic Theory of Gases 729 3.
Page 756 and 757:
U trans = 3 2 NkT (Continued ) 18.3
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18.4 Intermolecular Collisions 733
Page 760 and 761:
18.5 Molecular Velocity Distributio
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18.5 Molecular Velocity Distributio
Page 764 and 765:
18.6 Equipartition of Energy 739 We
Page 766 and 767:
18.7 Introduction to Mathematical P
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Page 770 and 771:
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18.8 Quantum Statistical Thermodyna
Page 774 and 775:
18.9 Three Classical Quantum Statis
Page 776 and 777:
18.11 Monatomic Maxwell-Boltzmann G
Page 778 and 779:
18.12 Diatomic Maxwell-Boltzmann Ga
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18.12 Diatomic Maxwell-Boltzmann Ga
Page 782 and 783:
18.13 Polyatomic Maxwell-Boltzmann
Page 784 and 785:
Summary 759 In this chapter, we sum
Page 786 and 787:
Problems 761 4. Find the temperatur
Page 788 and 789:
CHAPTER 19 Introduction to Coupled
Page 790 and 791:
19.3 Linear Phenomenological Equati
Page 792 and 793:
19.4 Thermoelectric Coupling 767 Eq
Page 794 and 795:
19.4 Thermoelectric Coupling 769 Th
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19.4 Thermoelectric Coupling 771 wh
Page 798 and 799:
19.4 Thermoelectric Coupling 773 Th
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19.4 Thermoelectric Coupling 775 b.
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19.5 Thermomechanical Coupling 777
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Page 806 and 807:
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water), it seems reasonable that li
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Problems 785 b. For a Knudson gas,
Page 812 and 813:
Appendix A: Physical Constants and
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Appendix B: Greek and Latin Origins
Page 816 and 817:
Appendix B 791 Table B.4 Plural End
Page 818 and 819:
Index Page numbers followed by f in
Page 820 and 821:
Index 795 E e (specific energy), 10
Page 822 and 823:
Index 797 Isobaric coefficient of v
Page 824 and 825:
Index 799 Ranque, Georges Joseph, 3
Page 826 and 827:
Index 801 William III, King of Engl
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Modern Engineering Thermodynamics

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