Engineering webinar material dealing with simple and basic Brayton Cycle and power cycle components/processes and their T - s diagrams, ideal and real operation and major performance trends when air is considered as the working fluid.
2. Energy Conversion Ideal vs Real Operation
Analysis Webinar Objectives
In this webinar, the engineering students and professionals get familiar with the simple
and basic power cycles, power cycle components/processes and compressible flow
and their T - s, p - V and h - T diagrams, ideal vs real operation and major
performance trends when air is considered as the working fluid.
Performance Objectives:
Introduce basic energy conversion engineering assumptions and equations
Know basic elements of Carnot Cycle, Brayton Cycle, Otto Cycle, Diesel Cycle,
compression, combustion and expansion processes and compressible flow (nozzle,
diffuser and thrust) and their T - s, p - V and h - T diagrams
Be familiar with Carnot Cycle, Brayton Cycle, Otto Cycle, Diesel Cycle, compression,
combustion, expansion and compressible flow (nozzle, diffuser and thrust) ideal vs
real operation
Understand general Carnot Cycle, Brayton Cycle, Otto Cycle, Diesel Cycle,
compression, combustion, expansion and compressible flow (nozzle, diffuser and
thrust) performance trends
3. This webinar consists of the following three major sections:
• Power Cycles (Carnot, Brayton, Otto and Diesel)
• Power Cycle Components/Processes (compression,
combustion and expansion)
• Compressible Flow (nozzle, diffuser and thrust)
In this webinar, first overall engineering assumptions and basic engineering
equations are provided. Furthermore, for each major section, basic
engineering equations, section material and conclusions are provided.
Energy Conversion Analysis Webinar
4. The energy conversion analysis presented in this webinar considers ideal (isentropic) vs real operation and the
working fluid is air. Furthermore, the following assumptions are valid:
Power Cycles
Single species consideration -- fuel mass flow rate is ignored and its impact on the properties of the working
fluid
Basic equations hold (continuity, momentum and energy equations)
Specific heat is constant
Power Cycle Components/Processes
Single species consideration
Basic equations hold (continuity, momentum and energy equations)
Specific heat is constant
Compressible Flow
Single species consideration
Basic equations hold (continuity, momentum and energy equations)
Specific heat is constant
Thermodynamic and Transport Properties
Single species consideration
Ideal gas approach is used (pv=RT)
Specific heat is not constant
Coefficients describing thermodynamic and transport properties were obtained from the NASA Glenn Research
Center at Lewis Field in Cleveland, OH -- such coefficients conform with the standard reference temperature of
298.15 K (77 F) and the JANAF Tables
Engineering Assumptions
5. Basic Conservation Equations
Continuity Equation
m = ρvA [kg/s]
Momentum Equation
F = (vm + pA)out - in [N]
Energy Equation
Q - W = ((h + v2/2 + gh)m)out - in [kW]
Basic Engineering Equations
6. Ideal Gas State Equation
pv = RT [kJ/kg]
Perfect Gas
cp = constant [kJ/kg*K]
Kappa
χ = cp/cv [/]
For air: χ = 1.4 [/], R = 0.2867 [kJ/kg*K] and
cp = 1.004 [kJ/kg*K]
Basic Engineering Equations
13. Brayton Cycle (Gas Turbine) Schematic Layout -- Open Cycle
Compressor
Combustor
Gas Turbine
1
32
4
Fuel
Brayton Cycle (Gas Turbine)
Heat Addition
Working Fluid In Working Fluid Out
20. Brayton Cycle (Gas Turbine) Specific Power
Output
0
100
200
300
400
500
900 1,200 1,500
Gas Turbine Inlet Temperature [K]
BraytonCycle(GasTurbine)SpecificPower
Output[kJ/kg]
85 90 95 100
Working Fluid: Air
Brayton Cycle (Gas Turbine)
Isentropic Expansion Efficiency [%]
Compressor Inlet Temperature: 298 [K] -- Gas Turbine Inlet Pressure: 15 [atm]
Compression Ratio (P2/P1) = 15 [/]
21. Brayton Cycle (Gas Turbine) Power Output
0
25
50
75
100
50 100 150
Working Fluid Mass Flow Rate [kg/s]
BraytonCycle(GasTurbine)PowerOutput[MW]
85 90 95 100
Working Fluid: Air
Brayton Cycle (Gas Turbine)
Isentropic Expansion Efficiency [%]
Compression Ratio (P2/P1) = 15 [/]
Gas Turbine Inlet Temperature: 1,500 [K] -- Gas Turbine Inlet Pressure: 15 [atm]
22. Brayton Cycle (Gas Turbine) Efficiency
0
20
40
60
80
5 10 15 20 25
Compression Ratio (P2/P1) [/]
BraytonCycle(GasTurbine)Efficiency[%]
85 90 95 100
Working Fluid: Air
Brayton Cycle (Gas Turbine)
Isentropic Compression and Expansion Efficiency [%]
Ambient Temperature: 298 [K] -- Gas Turbine Inlet Temperature: 1,500 [K]
23. Brayton Cycle (Gas Turbine) Specific Power
Output
0
100
200
300
400
500
900 1,200 1,500
Gas Turbine Inlet Temperature [K]
BraytonCycle(GasTurbine)SpecificPower
Output[kJ/kg]
85 90 95 100
Working Fluid: Air
Brayton Cycle (Gas Turbine)
Isentropic Compression and Expansion Efficiency [%]
Compressor Inlet Temperature: 298 [K] -- Gas Turbine Inlet Pressure: 15 [atm]
Compression Ratio (P2/P1) = 15 [/]
24. Brayton Cycle (Gas Turbine) Power Output
0
25
50
75
100
50 100 150
Working Fluid Mass Flow Rate [kg/s]
BraytonCycle(GasTurbine)PowerOutput[MW]
85 90 95 100
Working Fluid: Air
Brayton Cycle (Gas Turbine)
Isentropic Compression and Expansion Efficiency [%]
Compression Ratio (P2/P1) = 15 [/]
Gas Turbine Inlet Temperature: 1,500 [K] -- Gas Turbine Inlet Pressure: 15 [atm]
25. Otto Cycle p - V Diagram
1
3
2s
4s
Pressure--p[atm]
Volume -- V [m^3]
Otto Cycle
26. Otto Cycle T - s Diagram
1
3
2s
4s
Temperature--T[K]
Entropy -- s [kJ/kg*K]
Otto Cycle
2
4
27. Otto Cycle Efficiency
0
20
40
60
80
2.5 5 7.5 10 12.5
Compression Ratio (V1/V2) [/]
OttoCycleEfficiency[%]
85 90 95 100
Working Fluid: Air
Otto Cycle
Isentropic Compression Efficiency [%]
Ambient Temperature: 298 [K] -- Combustion Temperature: 1,200 [K]
28. Otto Cycle Power Output
0
100
200
300
400
1,200 1,500 1,800
Combustion Temperature [K]
OttoCyclePowerOutput[kW]
85 90 95 100
Compression Ratio (V1/V2) = 10 [/]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Otto Engine
Otto Cycle
Isentropic Compression Efficiency [%]
29. Otto Cycle Efficiency
0
20
40
60
80
2.5 5 7.5 10 12.5
Compression Ratio (V1/V2) [/]
OttoCycleEfficiency[%]
85 90 95 100
Working Fluid: Air
Otto Cycle
Isentropic Expansion Efficiency [%]
Ambient Temperature: 298 [K] -- Combustion Temperature: 1,200 [K]
30. Otto Cycle Power Output
0
100
200
300
400
1,200 1,500 1,800
Combustion Temperature [K]
OttoCyclePowerOutput[kW]
85 90 95 100
Compression Ratio (V1/V2) = 10 [/]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Otto Engine
Otto Cycle
Isentropic Expansion Efficiency [%]
31. Otto Cycle Efficiency
0
20
40
60
80
2.5 5 7.5 10 12.5
Compression Ratio (V1/V2) [/]
OttoCycleEfficiency[%]
85 90 95 100
Working Fluid: Air
Otto Cycle
Isentropic Compression and Expansion Efficiency [%]
Ambient Temperature: 298 [K] -- Combustion Temperature: 1,200 [K]
32. Otto Cycle Power Output
0
100
200
300
400
1,200 1,500 1,800
Combustion Temperature [K]
OttoCyclePowerOutput[kW]
85 90 95 100
Compression Ratio (V1/V2) = 10 [/]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Otto Engine
Otto Cycle
Isentropic Compression and Expansion Efficiency [%]
33. Diesel Cycle p - V Diagram
1
32s
4s
Pressure--p[atm]
Volume -- V [m^3]
Diesel Cycle
34. Diesel Cycle T - s Diagram
1
3
2s
4s
Temperature--T[K]
Entropy -- s [kJ/kg*K]
Diesel Cycle
2
4
36. Diesel Cycle Power Output
0
200
400
600
7.5 10 12.5 15 17.5
Compression Ratio (V1/V2) [/]
DieselCyclePowerOutput[kW]
85 90 95 100
Combustion Temperature: 1,800 [K]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Diesel Engine
Diesel Cycle
Isentropic Compression Efficiency [%]
38. Diesel Cycle Power Output
0
200
400
600
7.5 10 12.5 15 17.5
Compression Ratio (V1/V2) [/]
DieselCyclePowerOutput[kW]
85 90 95 100
Diesel Cycle
Isentropic Expansion Efficiency [%]
Combustion Temperature: 1,800 [K]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Diesel Engine
40. Diesel Cycle Power Output
0
200
400
600
7.5 10 12.5 15 17.5
Compression Ratio (V1/V2) [/]
DieselCyclePowerOutput[kW]
85 90 95 100
Diesel Cycle
Isentropic Compression and Expansion Efficiency [%]
Combustion Temperature: 1,800 [K]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Diesel Engine
41. Diesel Cycle Cut Off Ratio
0
1
2
3
4
7.5 10 12.5 15 17.5
Compression Ratio (V1/V2) [/]
DieselCycleCutOffRatio[/]
100
Diesel Cycle
Isentropic Compression and Expansion Efficiency [%]
Combustion Temperature: 1,800 [K]
Working Fluid: Air
Ambient Temperature: 298 [K] -- Number of Revolutions: 60 [1/s]
For Given Geometry of the Four Cylinder and Four Stroke Diesel Engine
42. Power Cycles Conclusions
The Carnot Cycle efficiency increases with an increase in the heat addition temperature when the heat rejection
temperature does not change at all. Furthermore, the Carnot Cycle efficiency decreases with an increase in the
heat rejection temperature when the heat addition temperature does not change at all. The Carnot Cycle
efficiency is not dependent on the working fluid properties.
The Brayton Cycle efficiency depends on the compression ratio values . The efficiency increases with an
increase in the compression ratio values for a fixed gas turbine inlet temperature. The Brayton Cycle specific
power output increases with an increase in the gas turbine inlet temperature for a fixed compression ratio.
Furthermore, the increase is greater for the higher gas turbine inlet temperature values.
The Brayton Cycle power output increases with an increase in the working fluid mass flow rate. The increase is
greater for the higher working fluid mass flow rate values for the fixed gas turbine inlet temperature and
compression ratio values.
The Otto Cycle efficiency increases with an increase in the compression ratio values for a fixed combustion
temperature. Also, the Otto Cycle power output increases with an increase in the combustion temperature for a
fixed compression ratio value and given geometry of the four cylinder and four stroke Otto engine.
The Diesel Cycle efficiency increases with an increase in the compression ratio and with a decrease in the cut
off ratio values for a fixed combustion temperature. Also, the Diesel Cycle power output increases with an
increase in the compression ratio values for a fixed combustion temperature value and given geometry of the
four cylinder and four stroke Diesel engine.
In general, as the isentropic compression and expansion efficiency values decrease, the cycle efficiency
decreases too.
44. Combustion is complete with and without heat loss and at
stoichiometric and stoichiometry > 1 conditions having different
oxidant preheat temperature and the oxidant is air.
Also,
Ideal Flame Temperature [K]
hreactants = hproducts [kJ/kg]
Real Flame Temperature [K]
hproducts = hreactants - heat loss [kJ/kg]
heat loss = (1 - combustion )HHV/(1 + oxidant to fuel ratio) [kJ/kg]
Power Cycle Components/Processes
Engineering Equations
111. Expansion T - s Diagram
Temperature--T[K]
Entropy -- s [kJ/kg*K]
Expansion
1
2s
2
112. Expansion Specific Power Output
400
500
600
700
800
900
5 10 15
Expansion Ratio (P1/P2) [/]
ExpansionSpecificPowerOutput[kJ/kg]
85 90 95 100
Working Fluid: Air
Turbine Inlet Temperature: 1,500 [K] -- Ambient Pressure: 1 [atm]
Expansion
Isentropic Expansion Efficiency [%]
113. Expansion Power Output
0
40
80
120
160
50 100 150
Working Fluid Mass Flow Rate [kg/s]
ExpansionPowerOutput[MW]
85 90 95 100
Working Fluid: Air
Turbine Inlet Temperature: 1,500 [K] -- Expansion Ratio (P1/P2): 15 [/]
Expansion
Isentropic Expansion Efficiency [%]
114. Power Cycle Components/Processes
Conclusions
The compression specific power input increases with an increase in the compression
ratio values for a fixed compression inlet temperature. As the working fluid mass flow
rate increases for the fixed compression ratio and compression inlet temperature
values, the compression power input requirements increase too. As the isentropic
compression efficiency decreases, the compression power input increases.
Hydrogen as the fuel has the highest flame temperature, requires the most mass
amount of oxidant/air in order to have complete combustion per unit mass amount of
fuel and has the largest fuel higher heating value. As the combustion efficiency
decreases, the combustion products flame temperature decreases.
When hydrogen reacts with oxidant/air, there is no CO2 present in the combustion
products.
The expansion specific power output increases with an increase in the expansion ratio
values for a fixed expansion inlet temperature. As the working fluid mass flow rate
increases for the fixed expansion ratio and expansion inlet temperature values, the
expansion power output values increase too. As the isentropic expansion efficiency
decreases, the expansion power output decreases.
115. Sonic Velocity
vsonic = (χ RT)1/2 [m/s]
Mach Number
M = v/vsonic [/]
Compressible Flow Engineering Equations
133. Compressible Flow Conclusions
Nozzle stagnation over static temperature and pressure ratio values increase with an
increase in the velocity (Mach Number).
Diffuser stagnation over static temperature and pressure ratio values increase with an
increase in the velocity (Mach Number).
Thrust increases with an increase in the inlet stagnation temperature.
As the nozzle and diffuser efficiency values decrease, the nozzle, diffuser and thrust
performance decreases.