Application of the Organic Rankine Cycle for DHC/CHP System
Campus Energy 2016 – The Changing Landscape 2016. 2. 8 ~ 12, JW Marriott Austin Hotel, Austin, TX
Jong Jun Lee, Shin Young Im Korea District Heating Corporation
Contents
♠ Introduction ♠ System Configuration ♠ Results
♠ Conclusion
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Introduction System Configuration Results Conclusion
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Introduction Research Background Increasing greenhouse effect and draining fossil fuel reserves
CO2 is main source of the greenhouse effect
More than 80% of CO2 emission comes from Power generation
Adoption of Paris Agreement at December 12, 2015 The United Nations framework convention on climate change(2℃ scenario)
South Korea should be reduced 37% CO2 Emission
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Background *International Energy Outlook 2013(DOE/IEA)
Fig.1 World energy consumptions
Fig.2 World energy-related carbon dioxide emissions
World marketed energy consumption is projected to grow by 56% than 2010 World carbon dioxide emissions are projected to rise by 46% than 2010
Improving conventional power generation system Performance are one of the solution to solve those problems www.kdhc.co.kr
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Background
Combined Heat & Power(CHP) System is one of the solution for using energy more efficiently High efficiency and low emissions comparing to conventional Electricity and heat generation
• Catalog of CHP Technologies, U.S. Environmental protection Agency CHP Partnership, 2008 • A decade of progress Combined Heat and Power, U.S. Department of Energy, 2009
Wasted heat are still generated from CHP www.kdhc.co.kr
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Background
Organic Rankine Cycle(ORC) The power generation system which Use Organic fluid as working fluid Additional electricity can be generated using lower temperature heat source
USA (Ormat)
Germany (GMK)
Italy (Turboden)
•Waste heat recovery projects using Organic Rankine Cycle technology, 2011, G. David, F. Michel, L. Sanchez
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Background
Pure Organic Rankine Cycle ORC
SRC
Temperature
70~350℃
350℃~
Efficiency
8~22%
30~40%
Output
100kW~5MW
1MW~
•ORC Products and applications Korea, Pratt & Whitney(Turboden) Brochure
Under 350℃ steam can be generate electricity by ORC SRC may more effective than ORC if the temperature of heat source are higher than 350℃ www.kdhc.co.kr
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Background
Pure Organic Rankine Cycle Organic Rankine Cycle Operating Temperature(R245fa)
3
212℉
(100℃)
2
3
4
4
86℉ 1
(30℃)
2
1-2 process : Compression 2-3 process : Heating 3-4 process : Expansion 4-1 process : Cooling(Condensing) www.kdhc.co.kr
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Background
Comparison between ORC & SRC Organic Rankine Cycle
Steam Rankine Cycle
Two-Phase Super-heating Sub-cooling
Condensing
•Kyoung hoon Kim, 2011, “Study of Working Fluids on Thermodynamic Performance of Organic Rankine Cycle (ORC),” Trans. of the Korean Hydrogen and New Energy Society(2011. 4), Vol. 22, No. 2, pp. 223~231 •Michael J. Moran & Howard N. Shapiro, 2000, Fundamentals of Engineering Thermodynamics 4th ed, John Wiley & Sons, Inc.
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction Research Objective
To Find out how to increasing CHP performance when ORC(organic rankine cycle) are adopted Developing Performance Simulation model using commercial simulation tools(GateCycle, Aspen Hysys) Combined Cycle and Organic Rankine Cycle models are validated using commercial CC CHP plant Proposing How to Adopt Organic Rankine Cycle to the conventional CC CHP Plant
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction System Configuration Results Conclusion
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System Configuration CC CHP Plant system diagram
System Configuration (CC CHP)
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
System Configuration System Modeling(CC CHP) Design specifications of GT(GE7EA) Component
Parameters
Modeling*
(oC)
15 101.3 294.6 12.8 17
Air temperature Inlet Air pressure (kPa) Air flow (kg/s) Pressure ratio Compressor Number of stages Polytropic efficiency (%) Combustor
Turbine
Component
Turbine
90
Parameters
Modeling*
Inlet temperature (oC)
449
Inlet pressure (kPa)
4848
Added flow pressure (kPa)
451
Isentropic efficiency (%)
87.8
Main steam flow (kg/s)
42.1
5.36
Pump
Input Efficiency (%)
85
Lower heating value (kJ/kg) of NG
49430
Deaerator
Outlet Pressure (kPa)
4.0
Turbine inlet temperature (oC)
1154
Mechanical efficiency (%)
99
Turbine exhaust temperature (oC)
548
Generator efficiency (%)
97
Fuel flow (kg/s)
Total coolant relative to compressor
Performance
Design specifications of HRSG and ST
Performance
14.3
inlet air flow (%) Power output (MW)
86.8
Thermal efficiency (%)
32.7
Exhaust gas
Power Generator output (MW)
31.7
Temperature (oC)
82.7
*Gas turbine world handbook. 2012. **GE-Energy. GateCycle ver 6.1.2
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
System Configuration ORC Plant system diagram
ORC System Configuration Organic fluid for working
=> ORC System working fluid : R245fa
Gas/Steam Water/Air HRU (Heat Recovery Unit) Heat Supply
Evapo rator
Tubine
Heat Exhaust
Econo mizer Condenser Pump
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
System Configuration System Modeling(ORC) Design specifications of ORC system* Parameters
Modeling
ORC Turbine Isentropic Efficiency (%)
80
Pump Isentropic Efficiency (%)
75
HRU Pinch Temperature(oC)
10
Condensing temperature(oC)
30
*Mago P. J., Chamra L. M., Srinivasan K., Somayaji C., 2008, "An examination of regenerative organic Rankine cycles using dry fluids," Applied Thermal Engineering Vol. 28 pp.998~1007.
Case 1 : Using stack exhaust gas as heat source of ORC(With DH Economizer) Case 2 : Using stack exhaust gas as heat source of ORC(Without DH Economizer) Case 3 : Using hot water(which delivering heat to consumer) as heat source of ORC
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction System Configuration Results Conclusion
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Results System Modeling(ORC-Case1)
ORC System Case 1 A
Organic fluid for working Steam Gas Cogeneration water
Steam Turbine Deaerator
DH heater #2
Fuel
Consumer
Combustor ORC Turbine
Comp.
Air
DH ECO
HRSG
HRU Condenser
Cooling Air
DH heater #1
Acuumulator
A
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Results Performance analysis result(Case1) Mass flow working fluid(kg/s)
400
ORC Net Power(kW)
350 300 250 200
20
𝑊 = 𝑚 × ∆ℎ
50
18 16
40
14 30 12 20
10 Mass flow(kg/s)
10
150
8
Turbine specific power (kJ/kg)
Results(Case 1)
60
Enthalpy change(kJ/kg) 0
Power
100
6 50
50 50
55
60
65
70
75
80
75
650
70
600
80
o
Outlet temperature of HRU hot side( C)
550
65
- HRU Gas Side exhaust temp. 58℃ - Operating pressure : 354kPa - working fluid flow rate : 37.5kg/s
450
o
TIT( C)
500 60 55 400
Fixed hot side inlet temperature(82oC) and increased hot
side exhaust temperature(decreasing heat transfer rate) Decreasing mass flow of working fluid(R245fa) (Because of changing saturated vapor pressure) Increasing enthalpy difference of ORC turbine inlet and exit 19
50
350 o
TIT( C) Evaporation Pressure(kPa)
45 40
50
55 60 65 70 75 o Outlet temperature of HRU hot side( C)
Evaporator pressure(kPa)
Maximum Power output (362kW) @
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55 60 65 70 75 o Outlet temperature of HRU hot side( C)
300 80
250
Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Results Performance analysis result(Case1) 180
160
140
Temperature(℃)
120
Hot Side
Pinch (Fixed)
Increasing Heat Transfer rate = Increasing flow rate
100
80
Changing Operating pressure = Decreasing specific power
60
40
20
0 1
1.2
1.4
1.6
1.8
2
Entropy (kJ/kgK)
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Results Performance analysis result(Case2)
ORC System Case 2 A
Organic fluid for working Steam Gas Cogeneration water
Steam Turbine Deaerator
DH heater #2
Fuel
Consumer
Combustor ORC Turbine
Comp.
Air
DH ECO
HRSG
HRU Condenser
Cooling Air
DH heater #1
Acuumulator
A
DH Economizer off
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Results Performance analysis result(Case2)
Results(Case 2) 160
ORC Net Power(kW)
2700 2600 2500 2400 2300 2200 Power(kW)
2100
150
50
55
60
65
70
75
80
o
25
140 130
20 120 110
15 Mass flow(kg/s) Enthalpy variation(kJ/kg)
100 90
2000
30
50
55 60 65 70 75 o Outlet temperature of HRU hot side( C)
80
Turbine specific power (kJ/kg)
Mass flow of working fluidkg/s)
2800
10
Outlet temperature of HRU hot side( C)
Maximum Power output (2,796kW) @
- HRU Gas Side exhaust temp. 70℃ - Operating pressure : 1,006kPa - working fluid flow rate : 113.6kg/s
Similar as case1, hot side inlet temperature 151℃
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Results Performance analysis result(Case3)
ORC System Case 3 A
Organic fluid for working
ma (Total hot water)
Steam Gas Cogeneration water
water mb (Hot to ORC)
Steam Turbine Deaerator
Fuel
DH heater #2
ORC Consumer
Combustor
Turbine
Comp.
Air
Condenser
DH ECO
HRSG
DH heater #1
Cooling Air
HRU
Acuumulator
A
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Results Performance analysis result(Case3)
Performance estimation for Case 3 Definition of Heat Ratio to ORC(X)
mb X (%) 100 ma (a Total DH supply water, b Supplied to the HRU)
Defining total hot water flow rate ma , Supplying flow rate for ORC mb Supplying entire hot water to the ORC(X= 100) Power is 6,754kW - Turbine Inlet Temperature : 54℃
- Working Fluid mass flow : 605.9kg/s
Power is depend on the supplying hot water into the ORC
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Introduction System Configuration Results Conclusion
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Conclusion
Simulating conventional CC CHP Plant Three method are proposed for applying ORC to the conventional CC CHP Plant Case 3 is best performance but it has to use a lot of consumer’s heat Case 2 is practically appropriate method When the ORC are considered like as case2, CHP efficiency may increase 0.77%(p), CO2 may decrease 2,397ton/year comparing to original CC CHP Plant
Future work Constructing concept prove ORC Power plant Test and validation simulation result www.kdhc.co.kr
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Campus Energy 2016 – The Charging Landscape February 8~12, 2016, JW Marriott Austin Hotel, TX
Thank You for Your Attention
Senior Researcher Jong Jun Lee E-mail :
[email protected] Office : 82-2-2040-1258 Cell : 82-10-4844-7247
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