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L/O/G/O
Thermodynamics Fundamental for TKEhttp://share.its.ac.id
Dosen :Syamsul [email protected]
K5
TEKNIK KONVERSI & KONSERVASI ENERGITF 091324 / 4 SKS / Smt. 6
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Energy Conversion
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Energy Source and Conversion Processes
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Energy Conversion Technologies
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Laws of Thermodynamics
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Entropy
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Carnot Heat Engine
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The Carnot Cycle
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Q1
Q2
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The Carnot Cycle
….1
….2
….3
Syamsul Arifin
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The Carnot Cycle
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Stirling Engine
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Stirling Engine
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Stirling Engine
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Thermodynamic Processes in β Configuration
Syamsul Arifin
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Thermodynamic Processes in β Configuration
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Thermodynamic Processes in a Ideal Stirling Cycle
Syamsul Arifin
Wout
Vmin
Vmax
TH
TL
QH
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Efficiency of an Ideal Stirling Cycle
Syamsul Arifin
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Mot
or B
akar
Dal
am
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Phase 1:Virtually all the gas is in the compression space at ambient temperature and the displacer is in the tip of the cold finger. In this phase the pistons are driven inwards, compressing the gas. This proces is nearly isothermal, the heat output Qc being dissipated via heat sinks around the compressor and the base of the cold finger. Phase 2:The pistons have reached the end of the compression stroke, the gas in the compression space is at ambient temperature and the displacer has not yet moved. This is the situation at the start of Phase II. Throughout this phase the pistons remain stationary and hence the total volume of gas remains constant. The displacer moves downwards as its spring compresses and gas flows through the regenerator, giving up heat Qr in the proces. This heat is stored in the renegeratoruntil later in the cycle. Phase 3:The pistons are driven outwards and the gas expands. This expansion process, too, is nearly isothermal, the heat input Qe being drawn from the surroundings of the expansion space. As a result refrigeration occurs at the tip of the cold finger. Phase 4:Throughout this phase the pistons remain stationary. The displacer, however, moves upwards because of the lower gas pressure in the expansion space. Gas from the expansion space therefor flows back through the regenerator, taking up the stored heat Qr in the process and re-entering the compression space at ambient temperature.
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Figure 1 - The Sunpower EG-1000 free-piston Stirling engine/generator
The linear electrical generator is comprised of powerful rare-earth magnets in the piston cutting a magnetic circuit and coils in the cylinder. This produces 240 Volts at 50 Herz - designed for operation in Europe, and is capable of producing more than one kilowatt of electrical power output at around 90% efficiency. The hot water is provided by operating the cooling water at a temperature of 50°C.
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In this photograph we see the Sunpower EG-1000 being demonstrated using sawdust pellets as the fuel, and generating more than 1000W of electricity to a light panel. This was done at the Sustainability Fair in the Fairgrounds of Athens Ohio, 2001. A closeup photograph of the basic system is shown. Notice the closed cycle radiator and vibration pump used in the water cooling system.
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Stirling Engine Analysis
Syamsul Arifin
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Stirling Engine Analysis
…..1
Syamsul Arifin
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Stirling Engine Analysis
…..2
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…..5Syamsul Arifin
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Stirling Engine Analysis
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…..12
Syamsul Arifin
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Stirling Engine Analysis
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Syamsul Arifin
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Stirling Engine Analysis
…..19
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Syamsul Arifin
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Stirling Engine Analysis
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Syamsul Arifin
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Stirling Engine Analysis
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Syamsul Arifin
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Stirling Engine Analysis
Syamsul Arifin
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Solar Dish Stirling System
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Solar Dish Stirling System Efficiency
Syamsul Arifin
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Rankin Cycle Engine
Syamsul Arifin
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Rankine Cycle Efficiency
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Ideal Reheat Rankine Cycle
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Organic Rankine Cycle
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Temperature Dependence of Rankine Cycle Devices
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Cycle Efficiencies with Heat Engines
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Organic Rankine Cycle
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Externally Heated Systems
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Cogeneration
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Internal Combustion EnginesAir Standard Cycles
Spark ignition
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Number of StrokesFour stroke
Two stroke
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Cylinder Design•Small engines usually have one or two cylinders, but may have as many as four.
Three Common Cylinder Orientations For Single Cylinder Engines
VerticalHorizontal
Slanted
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Cylinder Design-cont.
V
Horizontally opposed
In-line
Three common cylinder configuration in multiple cylinder engines:
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Hor izontal
Ver tical
Small gas engines use three crankshaft orientations:
Cylinder Design-cont.
Multi-position
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Otto Cycle P-V & T-s Diagrams
Pressure-Volume Temperature-Entropy
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Otto Cycle Derivation
• Thermal Efficiency:
– For a constant volume heat addition (andrejection) process;
– Assuming constant specific heat:
QQ - 1 =
QQ - Q =
H
L
H
LHthη
T C m = Q vin ∆
1-TTT
1 - TTT
-1 =)T - T( C m)T - T( C m - 1 =
2
32
1
41
23v
14vthη
Otto Cycle Derivation
T C m = Q v ∆Rej
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• For an isentropic compression (and expansion) process:
• where: γ = Cp/Cv
• Then, by transposing,
TT =
VV =
VV =
TT
4
3
3
41-
2
11-
1
2
γγ
TT =
TT
1
4
2
3
Otto Cycle Derivation
TT-1 =
2
1thηLeading to
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The compression ratio (rv) is a volume ratioand is equal to the expansion ratio in an ottocycle engine.
• Compression Ratio
VV =
VV = r
3
4
2
1v
1 + vv = r
vv + v =
volume Clearancevolume Total = r
cc
sv
cc
ccsv
where Compression ratio is defined as
Otto Cycle Derivation
![Page 54: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/54.jpg)
• Then by substitution,
)r(1 - 1 = )r( - 1 = 1-v
-1vth γ
γη
)r( = VV =
TT -1
v1
2-1
2
1 γγ
The air standard thermal efficiency of the Otto cycle then becomes:
Otto Cycle Derivation
![Page 55: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/55.jpg)
• Summarizing
QQ - 1 =
QQ - Q =
H
L
H
LHthη T C m = Q v ∆
1-TTT
1 - TTT
-1 =
2
32
1
41
thη
)r( = VV =
TT -1
v1
2-1
2
1 γγ
)r(1 - 1 = )r( - 1 = 1-v
-1vth γ
γη
TT =
TT
1
4
2
3
2
11TT th −=η
where
and then
Isentropic behavior
Otto Cycle Derivation
![Page 56: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/56.jpg)
• Heat addition (Q) is accomplished through fuel combustion
• Q = Lower Heat Value (LHV) BTU/lb, kJ/kg
Q AF m =Q
fuelain
cycle
Otto Cycle Derivation
T C m = Q vin ∆
also
![Page 57: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/57.jpg)
Otto Cycle Analysis
![Page 58: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/58.jpg)
• Determine the temperatures and pressures at each point in the Otto Cycle.
Compression Ratio = 9.5:1T1 temperature = 25oC = 298oKP1 pressure = 100 kPa
Otto Cycle P & T Prediction
![Page 59: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/59.jpg)
Diesel Cycle Derivation
![Page 60: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/60.jpg)
Diesel Cycle P-V & T-s Diagrams
![Page 61: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/61.jpg)
Diesel Cycle Derivation
• Thermal Efficiency (Diesel):
QQ - 1 =
QQ - Q =
H
L
H
LHthη
T C m = Q p ∆
For a constant pressure heat addition process;
For a constant volume heat rejection process;
T C m = Q v ∆
Assuming constant specific heat:
1-TTT
1 - TTT
- 1 =)T - T( C m)T - T( C m - 1 =
2
32
1
41
23p
14vth
γη where: γ = Cp/Cv
![Page 62: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/62.jpg)
• For an isentropic compression (and expansion) process:
• However, in a Diesel
• The compression ratio (rv) is a volume ratio and, in a diesel, is equal to the product of the constant pressure expansion and the expansion from cut-off.
TT =
VV
VV =
TT
4
3
3
41-
2
11-
1
2
γγ
VV
VV V = V
3
4
2
141 ≠
Diesel Cycle Derivation
![Page 63: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/63.jpg)
• Compression Ratio
• Then by substitution,VV
VV = r
3
4
2
1vc
≠vV
VV = r r = r
4
3
3
2ecpvc
••
( )
1)-r(1 - r
)r(1 - 1 =
cp
cp1-
vth γ
ηγ
γ
)r( = VV =
TT -1
v1
2-1
2
1 γγ
Diesel Cycle Derivation
![Page 64: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/64.jpg)
Diesel Cycle Analysis
![Page 65: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/65.jpg)
• Determine the temperatures and pressures at each point in the Diesel Cycle.
Compression Ratio = 20:1T1 temperature = 25oC = 298oKP1 pressure = 100 kPa
Diesel Cycle P & T Prediction
![Page 66: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/66.jpg)
Otto-Diesel Cycle Comparison
![Page 67: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/67.jpg)
Dual Cycle P-V Diagrams:
![Page 68: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/68.jpg)
• Dual Cycle Thermal Efficiency
5.2
3
VV
PP =
2
3 =βα
)T - T( C m + )T - T( C m = Q 2.53p22.5vin
1)-( + 1)-(1 -
CR1 - 1 =
1)-(
βγααβαη
γγ
Dual Cycle Efficiency
where: γ = Cp/Cv
( )14Rej TT C m = Q v −
![Page 69: syamsul@ep.its.ac.id K5 Thermodynamics Fundamental for TKE - Share …share.its.ac.id/pluginfile.php/9444/mod_resource/content/1/K5_Thermo1.pdf · Phase 1: Virtually all the gas is](https://reader030.vdocuments.net/reader030/viewer/2022040310/5d35ad7a88c993d6058bfb07/html5/thumbnails/69.jpg)
• Critical Relationships in the process include
)r( = VV =
TT -1
v1
2-1
2
1 γγ
Q AF m =
cycleQ
fuela
( )r = VV =
PP
v2
1
1
2 γγ
Diesel Cycle Derivation
T C m = Q p ∆ T C m = Q v ∆
( )
1)-r(1 - r
)r(1 - 1 =
cp
cp1-
vth γ
ηγ
γ