CHAPTER 9 Gas Power Cycles.

CHAPTER 9 Gas Power Cycles

9-1 Basic Considerations in the Analysis of Power Cycles
Air Standard Cycles The Spark Ignition Engine

Copyright © The McGraw-Hill Companies, Inc
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-1 Modeling is a powerful engineering tool that provides great insight and simplicity at the expense of some loss in accuracy.

General classes of engines
Reciprocating internal combustion engines. Reciprocating compressors Reciprocating steam engines

Single vs. double action engines
Single action reciprocating engine. Double action reciprocating engine.

Indicator diagrams An analog instrument that measures pressure vs.
Displacement in a reciprocating engine. The graph is in terms of P and V. p V Area is proportional to the work done per cycle

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-2 The analysis of many complex processes can be reduced to a manageable level by utilizing some idealizations.

FIGURE 9-6 P-v and T-s diagrams of a Carnot cycle.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-6 P-v and T-s diagrams of a Carnot cycle.

9-2 The Caront Cycle and Its Value in Engineering

FIGURE 9-7 A steady-flow Carnot engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-7 A steady-flow Carnot engine.

FIGURE 9-8 T-s diagram for Example 9–1.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-8 T-s diagram for Example 9–1.

9-3 Air Standard Assumptions
The working fluid is air, which continuously circulates in a closed loop and always behaves as an ideal gas. All the processes that make up the cycle are internally reversible. The combustion process is replaced by a heat-addition process from an external source. The exhaust process is replaced by a heat-rejection process that restores the working fluid to its initial state.

9-4 An Overview of Reciprocating Engines
Air Standard Cycles The Spark Ignition Engine

FIGURE 9-10 Nomenclature for reciprocating engines.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-10 Nomenclature for reciprocating engines.

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-12 The net work output of a cycle is equivalent to the product of the mean effective pressure and the displacement volume.

Indicator Diagrams Work per cycle is represented in terms of a mean effective pressure and the displacement. p V MEP = Mean effective pressure X = Displacement Mean Effective Pressure Concept The Mean Effective Pressure (MEP) is the average pressure that would exist if the engiene operatred at a constant pressure at the displacement of the engine. The rectangle in the diagram above has the same area as the actual indicator diagram in the previous illustration.

Work = MEP x A x Displacement.
Indicator Diagrams To compute the work per cycle, use the MEP and the displacement. Work = MEP x A x Displacement. MEP = kiY, where ki is a constant Y = the average ordinate on the indicator diagram. X = displacement A = area of cylinder heat.

Ideal indicator diagram Spark ignition engine - The Otto cycle
Processes: a-b Intake b-c Compression c-d Combustion (spark ignited) d-e Power Stroke e-f Gas Exhaust b-a Exhaust Stroke a b c d e p V Clearance volume Displacement

FIGURE 9-14 Schematic of a two-stroke reciprocating engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-14 Schematic of a two-stroke reciprocating engine.

The spark ignition engine - The Otto cycle

The Otto cycle The air standard Otto cycle approximates the automotive internal combustion engine and aircraft engines. Assume a quasistatic process, isentropic compression, and isentropic exhaust. p V 1 6 3 4 5 s = Constant 2 Displacement

The Otto cycle s = Constant T s V = Constant P-V diagram for the
This is the T-s diagram for the fixed mass system. s V = Constant T 6 3 4 5 2 p V 1 P-V diagram for the actual variable mass system. s = Constant

The air-standard Otto cycle
Real Process 1-2 Intake of fuel/air mixture at P1 2-3 Compression to P3 3-4 Combustion, V = cons. and increasing P 4-5 Expansion 5-6 Exhaust at constant V and falling pressure 6-1Exhaust at P1 Air Cycle Approximation (Constant mass, closed internally reversible, cycle) 2-3 Isentropic compression 3-4 Heat addition at constant volume 4-5 Isentropic expansion 5-6 Heat rejection at constant volume

The reversible Otto cycle
Internally reversible processes Constant specific heats k = Cp/Cv = Constant Polytropic compression and expansion, PVk = Const. Treat air as an ideal gas.

Thermodynamic analysis for the reversible Otto cycle
6 3 4 5 2 V = Constant s QH QC (1)

Thermodynamic analysis for the air-standard Otto Cycle
(2)

Thermodynamic Analysis for the air-standard Otto Cycle

Thermal efficiency

Thermal efficiency Key assumptions: (1) Internally reversible processes (2) Constant specific heats Important consequence: (1) Efficiency is independent of working fluid (2) Efficiency independent of temperatures

rv Efficiency of Air Standard Otto Cycle k = 1.3 = Cp/Cv T  s WNET
4 5 2,6 s QH QC

k = 1.4 k = 1.3

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-18 The thermal efficiency of the Otto cycle increases with the specific heat ratio k of the working fluid.

The Otto cycle with real gases
Variable specific heats. Efficiency based on internal energies obtained from the gas tables which take into account variable specific heats. T 3 4 5 2,6 V = Constant s QH QC

Air Standard Cycles The Compression Ignition Engine
9-6 Diesel Cycle: Air Standard Cycles The Compression Ignition Engine

The compression ignition engine - the Diesel cycle

Air Standard Compression Ignition Engine - The Diesel cycle
An IC power cycle useful in many forms of automotive transportation, railroad engines, and ship power plants. Key assumptions are, Constant specific heats, the ideal gas, and internally reversible processes.

Ideal Indicator Diagram Compression Ignition Engine
Processes: a-b Intake b-c Compression c-d Combustion d-e Power Stroke e-f Gas Exhaust b-a Exhaust Stroke Displacement Clearance volume a b c d e p V Indicator Card Work Indicator card work is the work done on the piston face and is usually greater than the work at the axle, or brake work. Thus for an engine, For a compressor

Ideal Indicator Diagram Compression Ignition Engine
Processes: a-b Combustion (P = Const.) b-c Expansion (s = Const) c-d Exhaust (V = Const) d-e Exhaust (P = Const) e-d Intake d-a Compression Displacement Clearance volume V a b c d e p Indicator Card Work Indicator card work is the work done on the piston face and is usually greater than the work at the axle, or brake work. Thus for an engine, For a compressor

FIGURE 9-21 T-s and P-v diagrams for the ideal Diesel cycle.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-21 T-s and P-v diagrams for the ideal Diesel cycle.

Advantages of the Diesel Cycle
Eliminates pre-ignition of the fuel-air mixture when compression ratio is high. All heat transfer to a constant mass system.

The air-standard compression ignition engine
b c d V = Constant p = Constant QH QC T s Wout Win

Thermal efficiency of the air- standard Diesel cycle
b c d V = Constant p = Constant QH QC s T

Key parameters for the Diesel cycle Compression Ratio Expansion Ratio
Displacement Clearance volume a b c d e p Key parameters for the Diesel cycle Compression Ratio Expansion Ratio V Cut Off Ratio

Thermal efficiency Displacement Clearance volume c d e p V a b

Air-standard Diesel cycle
p c d e Displacement Clearance volume V Thermal Efficiency Compression Ratio: Expansion Ratio: Cut Off Ratio: Air-standard Diesel cycle a b

Important features of the Diesel cycle
At rc = 1, the Diesel and Otto cycles have the same efficiency. Physical implication for the Diesel cycle: No change in volume when heat is supplied. A high value of k compensates for this. For rc > 1, the Diesel cycle is less efficient than the Otto cycle.

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-22 Thermal efficiency of the ideal Diesel cycle as a function of compression and cutoff ratios (k = 1.4).

Efficiency Comparisons (Approximate)
 rv rc = 1 rc > 1

Effect of variable specific heats
Efficiency is based on internal energies and enthalpies obtained from the gas tables which take into account variable specific heats.

Air-standard Diesel Cycle
Key terms and concepts Air-standard Diesel Cycle Expansion ratio Pressure ratio Cut of ratio Compression ignition

Comparison of the Otto and Diesel cycles

Comparison No. 1: (a) Same inlet state (P,V) (b) Same compression ratio, rv (c) Same QH Key factor: Constant volume heat addition of the Otto cycle vs. constant pressure heat addition of the Diesel cycle.

V p b c d a Displacement Otto cycle with a specified inlet condition at “a” with a given compression ratio rv = va/vb

same compression ratio, rv.
b c c* d* d a Displacement Otto and Diesel cycles with same compression inlet conditions at “a” and the same compression ratio, rv.

Diesel Cycle Otto Cycle p b c* d* d a V c

First Law analysis of the heat addition process
Otto: Heat addition with V = 0 in process b  c. W = 0, and P and T increase Diesel: Heat addition with P = Constant in process b  c*. dW > 0, and P and T lower that in the Otto cycle.

V = Const. T s d* d a b Tc Tc* P = Const. c c* Otto Cycle Diesel Cycle

T-s diagrams for equal heat addition
b Tc Tc* c* c The areas under the process paths b  c and b  c* are equal under the assumption of equal heat addition, QH. QH,Otto = QH,Diesel QH

Efficiency comparisons
When QH and rv are the same for both cycles, T s d* d a b Tc Tc* c* c QC,Otto < QC,Diesel

Comparison No. 2 is more practical when the “knocking” effect is considered. In the Otto cycle, about 11 atm are needed to achieve combustion with engine knock. Comparison No. 2: (a) Same inlet state (P,V) (b) Same maximum P (c) Same QH

T s d* d a b b* c* V = Const. P = Const. c Diesel Cycle Otto Cycle

Gas Power Systems - 3 The Dual Cycle

The Dual cycle The dual cycle is designed to capture capture some of the advantages of both the Otto and Diesel cycles. It it is a better approximation to the actual operation of the compression ignition engine.

p V d e a b c QH,P QH,V QC,V The Dual cycle s = Constant

FIGURE 9-23 P-v diagram of an ideal dual cycle.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-23 P-v diagram of an ideal dual cycle.

p QC,V V d e a b c QH,P QH,V

V d e a b c QH,P QH,V

Gas Power Systems - 4 The Gas Turbine

Overview Gas Turbines The Carnot cycle as an “air standard” cycle
The Ericcson Cycle The Brayton Cycle The standard cycle The reheat cycle Inter-cooling

The modern gas turbine cycle
Long-haul automotive power. Large aircraft flight envelopes Commercial aircraft Altitude (30,000 to 40,000 ft) Long range and low specific fuel consumption (sfc) Moderate speed and thrust

The modern gas turbine cycle
Military aircraft High altitude ( > 40,000 ft) Moderate range and high specific fuel consumption (sfc) High speed and large thrust Relevant cycles The Ericsson and Brayton cycles

General features of the aircraft gas turbine engine
Intake Air Fuel Compressor Turbine Combustor Exhaust Section Compressor Drive Shaft, Wcomp

The air-standard turbine cycle
Open system modeled as a closed system - fixed with fixed mass flow. Air is the working fluid. Ideal gas assumptions are applied. Approximate the combustor as the high temperature source. Internally reversible processes.

Ideal gas power cycles Air Standard Brayton Cycle Carnot Cycle Ericcson Cycle

Air-standard Carnot cycle

Air-standard Carnot cycle
Employ the same assumptions as for the air-standard turbine cycle. T s p1 p2 p3 p4 QH QC

Limitations of the air-standard Carnot cycle
Heat addition at constant temperature is difficult and costly. Work is required because fluid expands. Heat addition is limited because a large change in volume would imply a low mean pressure in the heat addition process. Frictional effects might become too great if the mean pressure is too low.

FIGURE 9-27 The execution of the Stirling cycle.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-27 The execution of the Stirling cycle.

Air-standard Ericsson cycle

FIGURE 9-28 A steady-flow Ericsson engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-28 A steady-flow Ericsson engine.

The air-standard Ericsson cycle
Constant pressure heat addition and rejection Constant temperature compression and expansion Qb-c v p a b c d T = Constant Qd-a Qc-d Qa-b

The Air Standard Ericcson Cycle
v p a b c d Qd-a Qc-d Qa-b Qb-c T = Const. The Air Standard Ericcson Cycle s T a b c d Qd-a Qc-d Qa-b Qb-c P = Const.

Thermal Efficiency Ericcson Cycle
Qb-c p a b c d T = Const. Qd-a Qc-d Qa-b Wc-d Wa-b v Thermal Efficiency Ericcson Cycle

The Brayton cycle

The Brayton Cycle Modern gas turbines operate on an open Brayton cycle. Ambient air is drawn at the inlet. Exhaust gases are released to the ambient environment. The air standard Brayton cycle is a closed cycle. All processes are internally reversible. Air is the working fluid and assumed an ideal gas.

General features of the aircraft gas turbine engine
Intake Air Fuel Compressor Turbine Combustor Compressor Drive Shaft, Wcomp Exhaust Gases & Work Output, Wturb

The open, actual cycle for the gas turbine.
The closed, air standard cycle for the gas turbine. QH QL WCOMP WTURB

The gas turbine processes
Isentropic compression to TH Constant pressure heat addition at TH Isentropic expansion to TC Constant pressure heat rejection at TC

Air Standard Brayton Cycle QH QL QC 2 3 WCOMP WTURB p V v 1 4 3 2
S = Constant QC 2 3 1 4

Air Standard Brayton Cycle QH QC p2 = p3 p1 = p4 T s 1 4 3 2 V p v
s = Constant s1 = s2 s3 = s4

Thermal efficiency of the ideal Brayton cycle
p2 = p3 p1 = p4 T s 1 4 3 2 QH QC WOUT WIN Thermal efficiency of the ideal Brayton cycle

Thermal Efficiency Ideal Brayton Cycle
For an ideal gas, h-h0 = Cp(T - T0). The compression and expansion process are polytropic with constant k. p2 = p3 p1 = p4 T s 1 4 3 2 QH QC WOUT WIN Thermal Efficiency Ideal Brayton Cycle

Cycle efficiency Ideal gas assumptions apply.
All processes internally reversible Compressor and turbine efficiency are each 100%. Assume fuel added in the combustor is a small percent (mass or moles) of total flow, and thus air properties provide a good estimate of cycle performance.

Real Turbine Performance
Gas Power Systems - 5 Real Turbine Performance

Internally irreversible Brayton cycles Real turbine performance
Overview Internally irreversible Brayton cycles Case study Real turbine performance

Internally irreversible Brayton cycles

Real cycle analysis - Brayton cycle
Internal irreversibility arises in each process of the open cycle. Compression (compressor efficiency) Heat addition Expansion (turbine efficiency)

Internal irreversibility will lower
work output and decrease thermal efficiency. Greater entropy production will also result. 2 3 1 4 p1 = p4 T,h p2 = p3 s s3 = s4

Case Study

Case study Given: Turbine and compressor efficiencies of 80%, and the operating data as given below. No internal irreversibility in the combustor. Find: For the actual cycle, the thermal efficiency, the ratio of Wcomp/Wturb and entropy production. QH QC WIN WOUT a b’ d’ c T s b d

Note: Values of h and so are from the gas tables, and all initial data are supplied here but this is not necessarily the case in practice.

Process Calculations Note: The pressure ratios for the isentropic and actual processes are the same, and therefore s = so.

Thermal Efficiency and Work Ratio
Notice that here we have a high ratio of the work of compression to that of expansion, which is typical in gas turbine systems. The key variable is the turbine inlet temperature, Tc, and this is to be made as large a possible. Tc is limited by the material and turbine blade cooling capability.

The entropy production rates are based on the application of the entropy balance for an open system to each process in the cycle. The heat addition and rejection processes are at the high and low temperatures respectively. Thus, these processes produce an entropy production from the external heat transfer process that is not included in the above calculations. Entropy Production

The Carnot Efficiency for the Cycle
QH, TH QC, TC (General cycle representation) Here, the difference in the efficiency calculations indicates a high level of external entropy production.

Efficiency Curves  T,h s s’2 s’4 Pressure Ratio, p2/p1
0.9 0.8 0.7 0.1 0.25 Brayton cycle efficiency is greatly dependent on the efficiencies of the turbine and compressor. The curves at the left are approximate. Efficiency Curves

FIGURE 9-29 An open-cycle gas-turbine engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-29 An open-cycle gas-turbine engine.

FIGURE 9-30 A closed-cycle gas-turbine engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-30 A closed-cycle gas-turbine engine.

FIGURE 9-31 T-s and P-v diagrams for the ideal Brayton cycle.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-31 T-s and P-v diagrams for the ideal Brayton cycle.

Gas Power Systems - 6 Cycle Improvements

Cycle Improvements Regeneration
Reduces heat input requirements and lowers heat rejected. Inter-cooling Lowers mean temperature of the compression process Reheat Raises mean temperature of the heat addition process

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-33 For fixed values of Tmin and Tmax , the net work of the Brayton cycle first increases with the pressure ratio, then reaches a maximum at rp = (Tmax /Tmin) k/[2(k – 1)], and finally decreases.

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-36 The deviation of an actual gas-turbine cycle from the ideal Brayton cycle as a result of irreversibilities.

The Brayton cycle with regeneration

FIGURE 9-38 A gas-turbine engine with regenerator.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-38 A gas-turbine engine with regenerator.

QH WTURB WCOMP The standard Brayton cycle shown as an open cycle. WIN
1 3 2 4 QH Regeneration is accomplished by preheating the combustor air with the exhaust gas from the turbine. WCOMP 5 WTURB WOUT

T,h s QH QC The maximum benefit of regeneration is obtained when
4 1 3 2 y Internal heat transfer, States 2 - x. QC QH s T,h The maximum benefit of regeneration is obtained when the exhaust temperature Ty is brought to temperature T2 by the regenerative heat exchanger.

T,h The ideal regenerator s QH QC 3 x 4 The ideal regenerator
1 3 2 y QC QH s T,h The ideal regenerator The ideal regenerator will heat the combustion air up to T4

The actual regenerator
3 The actual regenerator Actual internal heat transfer takes place between States 2 - x’. The effectiveness of the regenerator is the actual heat transfer divided by the maximum possible heat transfer. x 4 1 2 y QC QH s T,h

T,h Thermal efficiency s QH Regeneration reduces net heat input at the
high temperature. x 4 1 2 y QC QH s T,h 3 Thermal efficiency

FIGURE 9-39 T-s diagram of a Brayton cycle with regeneration.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-39 T-s diagram of a Brayton cycle with regeneration.

The Brayton cycle with inter-cooling

The standard Brayton cycle with on stage of inter-cooling
4 5 1 WCOMP WTURB QH 3 7 6

One stage of inter-cooling with turbine and compressor inefficiencies.
1 7’ 7 6 5’ 5 4 4’ 3 One stage of inter-cooling with turbine and compressor inefficiencies.

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-42 Comparison of work inputs to a single-stage compressor (1AC) and a two-stage compressor with intercooling (1ABD).

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-43 A gas-turbine engine with two-stage compression with intercooling, two-stage expansion with reheating, and regeneration.

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-45 As the number of compression and expansion stages increases, the gas-turbine cycle with intercooling, reheating, and regeneration approaches the Ericsson cycle.

The Brayton cycle with reheat

The re-heating of the fluid at an intermediate
pressure raises the enthalpy input to the cycle without raising the temperature of the external thermal reservoir. 4 1 3 2 5 s T,h 6

Example

In an air-standard gas turbine engine, air at 60o F
Description: In an air-standard gas turbine engine, air at 60o F and 1 atm enters the compressor with a pressure ratio of 5:1. The turbine inlet temperature is 1500o F, and the exhaust pressure is 1 atm. Determine the ratio of turbine work to compressor work and the thermal efficiency under the following operating conditions. This example compares several modifications to the basic Brayton cycle: multi-stage compression and expansion with reheat, inter-cooling and regeneration.

Operating conditions:
(a) The engine operates on an ideal Brayton cycle. (b) The adiabatic efficiency of the turbine and compressor are 0.83 and 0.93, respectively. (c ) The conditions of (b) hold and a regenerator with an effectiveness of 0.65 is introduced.

Operating conditions:
(d) The conditions of (b) and (c ) hold, and an inter-cooler that cools the air to 60o F at a constant pressure of 35 psia is added. (e) The inter-cooler is removed and a re-heater the heats the fluid to 1500o F at a constant pressure of 35 psia is added. (f) The conditions of (e) hold and the inter- cooler of (d) is put back.

(1) All cycles operate on the air-standard basis. (2) Ideal gas
Assumptions: (1) All cycles operate on the air-standard basis. (2) Ideal gas (3) Constant specific heats; k = constant, Cp = 0.24 BTU/lbm-R, k = 1.40 = constant. (4) Internally reversible processes except where isentropic efficiency (adiabatic efficiency) is less than one. (5) 1 atm = 14.7 psia.

(a) The engine operates as an ideal Brayton cycle.
Solution: (a) The engine operates as an ideal Brayton cycle. T s 1 2 3 4

Process quantities

(b) The adiabatic efficiency of the compressor and turbine
are 0.83 and 0.92 respectively. T s 1 2 3 4 2’ 4’

(c) The conditions of (b) hold, and a regenerator with
an effectiveness of 0.65 is introduced. 4’ T s 1 2 3 y 2’ x

(d) The conditions of (b) and (c ) hold, and an inter-cooler
that cools the air to 60o F at 35 psia is added. 520 R s 3 T 1 7’ 6 5’ 4’ P = 35 psia x y

s s 3 T 1 7’ 6 5’ 4’ x y Compute T5’ ,T7’, and the actual
520 R s 3 T 1 7’ 6 5’ 4’ P = 35 psia x y Compute T5’ ,T7’, and the actual temperature between state 7’ and x due to regeneration (7”). s

3 T 1 7’ 6 5’ 4’ P = 35 psia x y s

(e) Eliminate inter-cooling but add one stage of reheat
to 1500o F. (f) Combine parts (d) and (e).

Summary of results:

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-48 Basic components of a turbojet engine and the T-s diagram for the ideal turbojet cycle. [Source: The Aircraft Gas Turbine Engine and Its Operation. © United Aircraft Corporation (now United Technologies Corp.), 1951, 1974.]

FIGURE 9-52 A turbofan engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-52 A turbofan engine. [Source: The Aircraft Gas Turbine and Its Operation. © United Aircraft Corporation (now United Technologies Corp.), 1951, 1974.]

Photo Courtesy of Pratt&Whitney Corp.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-53 A modern jet engine used to power Boeing 777 aircraft. This is a Pratt & Whitney PW4084 turbofan capable of producing 84,000 pounds of thrust. It is 4.87 m (192 in.) long, has a 2.84 m (112 in.) diameter fan, and it weighs 6800 kg (15,000 lbm). Photo Courtesy of Pratt&Whitney Corp.

FIGURE 9-54 A turboprop engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-54 A turboprop engine. [Source: The Aircraft Gas Turbine Engine and Its Operation. © United Aircraft Corporation (now United Technologies Corp.), 1951, 1974.]

FIGURE 9-55 A ramjet engine.
Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-55 A ramjet engine. [Source: The Aircraft Gas Turbine Engine and Its Operation. © United Aircraft Corporation (now United Technologies Corp.), 1951, 1974.]

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-57 Under average driving conditions, the owner of a 30-mpg vehicle will spend $300 less each year on gasoline than the owner of a 20-mpg vehicle (assuming $1.50/gal and 12,000 miles/yr).

Copyright © The McGraw-Hill Companies, Inc. Permission required for reproduction or display. FIGURE 9-62 Aerodynamic drag increases and thus fuel economy decreases rapidly at speeds above 55 mph. (Source: EPA and U.S. Dept. of Energy.)

CHAPTER 9 Gas Power Cycles.

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