WO2011136118A1 - Dispositif de production de puissance à récupération de rejet thermique et navire pourvu dudit dispositif - Google Patents

Dispositif de production de puissance à récupération de rejet thermique et navire pourvu dudit dispositif Download PDF

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Publication number
WO2011136118A1
WO2011136118A1 PCT/JP2011/059806 JP2011059806W WO2011136118A1 WO 2011136118 A1 WO2011136118 A1 WO 2011136118A1 JP 2011059806 W JP2011059806 W JP 2011059806W WO 2011136118 A1 WO2011136118 A1 WO 2011136118A1
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Prior art keywords
heat recovery
exhaust heat
exhaust
heat
path
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PCT/JP2011/059806
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English (en)
Japanese (ja)
Inventor
雅幸 川見
芳弘 市来
渡辺　昌彦
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三菱重工業株式会社
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Priority to CN2011800168948A priority Critical patent/CN102834591A/zh
Priority to KR1020127024546A priority patent/KR20120136366A/ko
Publication of WO2011136118A1 publication Critical patent/WO2011136118A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J2/00—Arrangements of ventilation, heating, cooling, or air-conditioning
    • B63J2/02—Ventilation; Air-conditioning
    • B63J2/04—Ventilation; Air-conditioning of living spaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using kinetic energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J2/00—Arrangements of ventilation, heating, cooling, or air-conditioning
    • B63J2/12—Heating; Cooling
    • B63J2002/125—Heating; Cooling making use of waste energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2590/00—Exhaust or silencing apparatus adapted to particular use, e.g. for military applications, airplanes, submarines
    • F01N2590/02—Exhaust or silencing apparatus adapted to particular use, e.g. for military applications, airplanes, submarines for marine vessels or naval applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T70/00—Maritime or waterways transport
    • Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system

Definitions

  • the present invention relates to an exhaust heat recovery power generation apparatus that recovers exhaust heat from an internal combustion engine to generate electric power, and a ship equipped with the same.
  • Patent Document 1 listed below discloses an exhaust heat recovery power generator that generates power by an organic Rankine Cycle using exhaust heat from a diesel generator as a heat source. This document mainly describes heat recovery from exhaust gas from a diesel generator, and also shows that in the case of a water-cooled diesel engine, the engine cooling water (jacket cooling water) can be used. Has been.
  • the engine coolant has a temperature level of 80 to 90 ° C. at most, and there is a problem that the temperature level is low as a heat source for driving the organic Rankine cycle.
  • the temperature level is low as a heat source for driving the organic Rankine cycle.
  • steam turbines and power turbines gas turbines
  • using the exhaust gas from the marine main engine as a heat source for the organic Rankine cycle is not necessarily a good measure for achieving highly efficient heat recovery.
  • the present invention has been made in view of such circumstances, and the exhaust heat of the engine cooling water, which has a lower temperature level than the exhaust gas of the internal combustion engine and has a low utility value, is used as the heat source of the organic Rankine cycle.
  • An object of the present invention is to provide an exhaust heat recovery power generator that can be used and a ship equipped with the same.
  • an exhaust heat recovery power generator includes an engine cooling water that cools an internal combustion engine body, and an air cooler that cools compressed air discharged from a supercharger of the internal combustion engine.
  • the organic fluid is evaporated in an evaporator, then expanded in a turbine, and condensed in a condenser, that is, an organic Rankine cycle is performed.
  • the heat recovered from the engine cooling water and the air cooler is used as the heat source of the organic Rankine cycle.
  • the engine cooling water for example, 80 to 90 ° C.
  • the air cooler that have a lower temperature level than the exhaust gas and have not been used effectively (For example, 130 to 140 ° C.) can be used.
  • the temperature level of the heat source that drives the organic Rankine cycle is low only with engine cooling water, heat recovery is also performed from the air cooler, thereby enhancing the feasibility of power generation by the organic Rankine cycle.
  • a typical example of the internal combustion engine is a marine diesel engine (main engine). However, it is not limited to marine use but may be a land-use internal combustion engine used for power generation, for example.
  • the exhaust heat recovery from the air cooler is preferably performed from the upstream side (high temperature side) of the compressed air.
  • the engine cooling water includes jacket cooling water flowing through the cylinder jacket of the internal combustion engine body.
  • the exhaust heat recovery path includes a first exhaust heat recovery unit that exchanges heat with the engine coolant, and a second exhaust heat as the air cooler. And a waste heat recovery medium heat recovered by the first exhaust heat recovery device and the second exhaust heat recovery device exchanges heat with the organic fluid in the evaporator.
  • the exhaust heat recovery medium for example, water
  • the exhaust heat recovery medium flowing through the exhaust heat recovery path recovers exhaust heat from the engine cooling water in the first exhaust heat recovery device, and further recovers exhaust heat from the compressed air in the second exhaust heat recovery device. Later, the organic fluid was evaporated in an evaporator. As described above, the exhaust heat recovery medium recovered from the engine cooling water and the compressed air is directly guided to the evaporator without passing through another heat medium, so that the recovered heat can be guided to the evaporator with little heat loss.
  • the exhaust heat recovery path uses the engine cooling water as an exhaust heat recovery medium and performs heat exchange between the engine cooling water and the compressed air.
  • a third exhaust heat recovery device as the air cooler is provided, and the engine coolant recovered by the third exhaust heat recovery device exchanges heat with the organic fluid in the evaporator.
  • the engine coolant flowing through the exhaust heat recovery path collects exhaust heat from the air cooler in the third exhaust heat recovery unit, and then the organic fluid is evaporated in the evaporator.
  • the heat exchanger that exchanges heat with the engine cooling water (the first exhaust heat recovery device of the above invention) is omitted. And a simplified structure can be realized. Further, since the engine coolant recovered from the air cooler is directly guided to the evaporator without passing through another heat medium, the recovered heat can be guided to the evaporator with little heat loss.
  • the exhaust medium includes a heat medium circulation path through which the heat medium circulates and heat exchange with the organic fluid in the evaporator, and the exhaust heat recovery path Are a first exhaust heat recovery unit that exchanges heat with the engine coolant, a second exhaust heat recovery unit as the air cooler, the first exhaust heat recovery unit, and the second exhaust heat recovery unit.
  • the exhaust heat recovery medium recovered by heat exchanges heat with the heat medium in the heat medium circulation path.
  • the exhaust heat recovery medium flowing through the exhaust heat recovery path recovers exhaust heat from the engine cooling water in the first exhaust heat recovery device, and further recovers exhaust heat from the air cooler in the second exhaust heat recovery device.
  • Heat exchange with the heat medium (for example, water or heat medium oil) in the medium circulation path was performed.
  • the organic fluid was evaporated in the evaporator by the heat medium that received the recovered heat. In this way, the recovered heat may be guided to the organic fluid through the heat medium circulation path.
  • the exhaust medium includes a heat medium circulation path through which the heat medium circulates and heat exchange with the organic fluid in the evaporator, and the exhaust heat recovery path Comprises a third exhaust heat recovery device as the air cooler that uses the engine cooling water as an exhaust heat recovery medium and exchanges heat between the engine cooling water and the compressed air.
  • the engine cooling water recovered by the heat exchanger exchanges heat with the heat medium in the heat medium circulation path.
  • the engine coolant flowing through the exhaust heat recovery path recovers the exhaust heat from the air cooler in the third exhaust heat recovery unit, heat exchange with the heat medium (for example, water or heat transfer oil) in the heat medium circulation path; did. Then, the organic fluid was evaporated in the evaporator by the heat medium that received the recovered heat. In this way, the recovered heat may be guided to the organic fluid through the heat medium circulation path.
  • the heat exchanger the first exhaust heat recovery device of the above invention
  • the exhaust heat recovery power generator includes a steam turbine generator driven by steam generated by an exhaust gas heat exchanger that exchanges heat with the exhaust gas of the internal combustion engine.
  • the exhaust gas from an internal combustion engine having a high temperature level of 250 ° C. or higher is generated by a steam turbine that can be expected to have high efficiency.
  • exhaust heat recovery power generation can be performed with high efficiency over a wide temperature range.
  • the exhaust gas heat exchanger includes an evaporation unit that evaporates feed water, and an overheating unit that superheats steam generated in the evaporation unit
  • the exhaust heat recovery path includes a fourth exhaust heat recovery device that exchanges heat with the steam obtained in the evaporation section.
  • the steam obtained in the evaporation part of the exhaust gas heat exchanger (exhaust gas economizer) and the exhaust heat recovery medium are heat-exchanged. it can.
  • the exhaust heat recovery power generator includes a gas turbine generator driven by the exhaust gas of the internal combustion engine.
  • the internal combustion engine exhaust gas having a high temperature level of 250 ° C. or higher is generated by a gas turbine (power turbine) that can be expected to have high efficiency.
  • gas turbine power turbine
  • exhaust heat recovery power generation can be performed with high efficiency over a wide temperature range.
  • it can be made still more efficient by combining with a steam turbine generator.
  • the ship according to the second aspect of the present invention is characterized by including any one of the exhaust heat recovery power generation devices described above.
  • the ship according to the second aspect includes any one of the exhaust heat recovery power generation devices described above, it is possible to provide a highly energy-saving ship that can effectively recover exhaust heat.
  • the heat recovered from the engine cooling water and the air cooler is used as a heat source for driving the organic Rankine cycle.
  • the heat recovered from the engine cooling water and the air cooler is used as a heat source for driving the organic Rankine cycle.
  • FIG. 1 is a diagram schematically illustrating an exhaust heat recovery power generator according to a first embodiment of the present invention. It is the figure which showed roughly the exhaust-heat-recovery power generator concerning 2nd Embodiment of this invention. It is the figure which showed roughly the exhaust-heat-recovery power generation apparatus concerning 3rd Embodiment of this invention. It is the figure which showed roughly the exhaust-heat-recovery power generator concerning 4th Embodiment of this invention. It is the figure which showed roughly the exhaust-heat recovery electric power generating apparatus concerning 5th Embodiment of this invention. It is the figure which showed roughly the exhaust-heat recovery electric power generating apparatus concerning 6th Embodiment of this invention.
  • FIG. 1 schematically shows an exhaust heat recovery power generator according to a first embodiment of the present invention.
  • the exhaust heat recovery power generator includes a preheater (first exhaust heat recovery device) 1 that recovers heat from jacket cooling water (engine cooling water) that flows in a cylinder jacket 2 that cools a cylinder block and the like of a diesel engine, and a diesel engine
  • a first air cooler (second exhaust heat recovery device) 5 that recovers heat by cooling the compressed air discharged from the supercharger, and a heat medium that receives exhaust heat from the preheater 1 and the first air cooler 5
  • region enclosed with the dashed-two dotted line has shown the electric power generating apparatus 10 for organic Rankine cycles.
  • the organic Rankine cycle power generation device 10 by installing the organic Rankine cycle power generation device 10 on an existing ship, further exhaust heat recovery can be easily added.
  • the jacket cooling water flowing in the cylinder jacket 2 is circulated in the jacket cooling water circulation passage 14 by the jacket cooling water pump 12.
  • the jacket cooling water circulation passage 14 is formed so that the jacket cooling water flows in the order of the cylinder jacket 2, the preheater 1, the temperature adjusting three-way valve 16, and the jacket cooling water pump 12.
  • the jacket cooling water circulation passage 14 is provided with a bypass passage 23 through which the jacket cooling water bypasses the preheater 1.
  • the flow rate of the jacket cooling water flowing to the preheater 1 can be adjusted by adjusting the flow rate flowing through the bypass passage 23 with a bypass valve (not shown).
  • the temperature adjusting three-way valve 16 operates so that the jacket cooling water flowing into the cylinder jacket 2 has a desired inlet temperature. Specifically, when the inlet temperature at which the jacket cooling water flows into the cylinder jacket 2 is higher than a set value, fresh water of about 30 ° C. guided from the second air cooler 18 is supplied to the jacket cooling water circulation passage 14. Operates to flow more.
  • a branch flow path 22 that branches to the fresh water pump 20 is provided on the upstream side of the temperature adjusting three-way valve 16. The jacket cooling water flowing in the jacket cooling water circulation channel 14 from the branch channel 22 is discharged to the fresh water pump 20 side, so that the mass balance of the circulation flow rate flowing in the jacket cooling water circulation channel 14 is maintained. It has become.
  • the second air cooler 18 is installed on the downstream side of the first air cooler 5 with respect to the flow of compressed air discharged from the supercharger. Therefore, the first air cooler 5 is installed so as to have a higher temperature level than the second air cooler 18.
  • the fresh water flowing in the second air cooler 18 is guided after being cooled by a central cooler (not shown). Part of the fresh water whose compressed air has been cooled by the second air cooler 18 is guided to the temperature adjusting three-way valve 16, and the remaining part is returned again to the central cooler by the fresh water pump 20.
  • the exhaust heat recovery path 7 is a closed circuit, and an exhaust heat recovery pump 24 for circulating the heat transfer water is provided.
  • the heat transfer water is circulated by the exhaust heat recovery pump 24 so as to exchange heat with the preheater 1, the first air cooler 5, and the evaporator 30.
  • the temperature of the heat medium water inlet of the evaporator 30 is about 130 to 140 ° C., for example.
  • the organic fluid is evaporated by the heat transfer water.
  • the organic fluid path 9 As the organic fluid flowing through the organic fluid path 9, low molecular hydrocarbons such as isopentane, butane and propane, R134a and R245fa used as refrigerants, and the like can be used.
  • the organic fluid path 9 is a closed circuit, and an organic fluid pump 31 for circulating the organic fluid is provided.
  • the organic fluid circulates while repeating the phase change so as to pass through the evaporator 30, the power turbine 32, the economizer 34, and the condenser 36.
  • the power turbine 32 is rotationally driven by a heat drop (enthalpy drop) of the organic fluid evaporated by the evaporator 30.
  • the rotational power of the power turbine 32 is transmitted to the generator 38 so that electric power can be obtained by the generator 38.
  • the electric power obtained by the generator 38 is supplied to the inboard system via a power line (not shown).
  • the organic fluid (gas phase) that has finished work in the power turbine 38 preheats the organic fluid (liquid phase) sent from the organic fluid pump 31 in the economizer 34.
  • the organic fluid that has passed through the economizer 34 is cooled by seawater in the condenser 36 to be condensed and liquefied.
  • the condensed and liquefied organic fluid is sent to the economizer 34 and the evaporator 30 by the organic fluid pump 31.
  • the organic fluid path 9 constitutes an organic Rankine cycle together with the evaporator 30, the power turbine 32, the economizer 34, and the condenser 36.
  • the jacket cooling water led to the cylinder jacket 2 by the jacket cooling water pump 12 is heated by cooling the cylinder block or the like by the cylinder jacket 2 and then led to the preheater 1.
  • the preheater 1 heat exchange is performed between the heat transfer medium flowing through the exhaust heat recovery path 7 and the jacket cooling water, and the sensible heat of the jacket cooling water is recovered into the heat transfer medium in the exhaust heat recovery path 7. .
  • the temperature of the heat transfer water after heat recovery from the jacket cooling water is, for example, 80 to 90 ° C.
  • the air compressed by the turbocharger of the diesel engine is cooled by the first air cooler 5.
  • the heat medium water in the exhaust heat recovery path 7 flowing in the first air cooler 5 is heated by the compressed air, thereby recovering heat from the compressed air.
  • the temperature of the heat transfer water after heat recovery by the first air cooler 5 is set to 130 to 140 ° C., for example.
  • the heat transfer water that has recovered the exhaust heat by the preheater 1 and has recovered the exhaust heat by the first air cooler 5 and has reached a high temperature is led to the evaporator 30 and circulates in the organic fluid path 9. Exchange heat with.
  • the organic fluid is heated and evaporated by the sensible heat of the heat transfer water in the evaporator 30.
  • the organic fluid which has evaporated and becomes high enthalpy is guided to the power turbine 32, and the power turbine 32 is driven to rotate by the heat drop. Rotational output of the power turbine 32 is obtained, and power generation is performed by the generator 38.
  • the organic fluid (gas phase) that has finished the work in the power turbine 32 is preheated to the organic fluid (liquid phase) before flowing into the evaporator 30 by the economizer 34, and then led to the condenser 36, where seawater or the like It is condensed and liquefied by being cooled by the cooling water.
  • the jacket cooling water (engine cooling water) and the heat recovered by the first air cooler 5 were used.
  • jacket cooling water for example, 80 to 90 ° C.
  • a cooler eg, 130-140 ° C.
  • heat recovery is also performed from the first air cooler 5 to increase the feasibility of power generation by the organic Rankine cycle.
  • the heat transfer water flowing through the exhaust heat recovery path 7 recovers exhaust heat from the jacket cooling water, and further recovers exhaust heat with the first air cooler 5, and then evaporates the organic fluid with the evaporator 30. It was. In this way, since the jacket coolant and the heat transfer water recovered from the first air cooler 5 are directly guided to the evaporator 30 without passing through another heat transfer medium, the recovered heat is transferred to the evaporator 30 with less heat loss. Can lead.
  • the jacket cooling water heated by cooling the cylinder jacket 2 flows to the preheater 1, and the heat transfer water circulating through the exhaust heat recovery system 7 by the exhaust heat recovery pump 24 Exchange heat.
  • the heat transfer water recovered from the exhaust heat by the preheater 1 is guided to the first air cooler 5 and is heated after removing the compression heat from the compressed air discharged from the supercharger 40, and then evaporated. Guided to vessel 30.
  • the organic fluid that has been heated and evaporated by the heat transfer medium in the evaporator 30 drives the power turbine 32, and thereby the power generator 38 generates power.
  • the electric power generated by the generator 38 is frequency-adjusted by the inverter device 42 and then guided to the inboard system 44.
  • the exhaust gas from the diesel engine that is the main engine for propulsion is led to an exhaust gas economizer (exhaust gas heat exchanger) 46.
  • the exhaust gas economizer 46 recovers sensible heat of the exhaust gas, generates superheated steam in the superheater 48, and drives the steam turbine 50.
  • An exhaust gas power turbine (gas turbine) 54 is connected to the steam turbine 50 via a clutch 52.
  • the exhaust gas power turbine 54 is driven by exhaust gas guided from an exhaust manifold 56 of the diesel engine.
  • the rotation output obtained by the steam turbine 50 and the power turbine 54 is transmitted to the generator 60 via the speed reducer 58, and the generator 60 generates power.
  • the electric power generated by the generator 60 is output to the inboard system 44.
  • a plurality (three in FIG. 2) of power generation diesel engines 62 and a generator 64 are connected to the inboard system 44 in parallel. These power generation diesel engines 62 are started and stopped in accordance with the onboard power demand. Further, a shaft generator motor 66 is connected to the inboard system 44. The shaft generator motor 66 is configured to obtain electric power from the inboard system 44 and to energize the ship propeller 68, while collecting power from the ship propeller 68 to generate electric power to the inboard system 44. Can be powered.
  • the steam turbine 50 that can expect high efficiency is generated for exhaust gas from a ship propulsion diesel engine with a high temperature level of, for example, 250 ° C or higher. It was.
  • exhaust heat recovery power generation can be performed with high efficiency over a wide temperature range.
  • the exhaust gas power turbine 54 driven by the exhaust gas is further provided to generate power, exhaust heat recovery power generation can be realized with higher efficiency.
  • power generation is performed using both the steam turbine 50 and the exhaust gas power turbine 54.
  • the present invention is not limited to this, and only the steam turbine 50 or only the exhaust gas power turbine 54 is used. It is also good.
  • the exhaust gas economizer 46 is provided with an evaporator 49 located on a lower temperature side (a downstream side of the exhaust gas flow) than the superheater 48.
  • the vapor evaporated in the evaporator 49 is guided to the vapor drum 72.
  • the steam staying above the steam drum 72 is guided to a heater (fourth exhaust heat recovery device) 70.
  • the heater 70 the heat transfer water flowing through the exhaust heat recovery system 7 is heated and guided to the evaporator 30.
  • the heating temperature of the organic refrigerant in the evaporator 30 can be raised. .
  • the electric power generation by an organic Rankine cycle can be made highly efficient.
  • the steam obtained by the exhaust gas economizer 46 can be used effectively, the exhaust heat recovery power generation can be made more efficient.
  • symbol 3 has shown the diesel engine for ship propulsion, and the cylinder jacket 2 is typically shown by the side.
  • Reference numeral 74 denotes a steam turbine condenser connected to the downstream side of the steam turbine 50
  • reference numeral 76 denotes a condensate pump
  • reference numeral 78 denotes a ground condenser
  • reference numeral 80 denotes an atmospheric pressure condenser
  • reference numeral 82 denotes a water supply pump.
  • reference numeral 84 denotes a boiler drum water circulation pump that sends water in the steam drum 72 to the evaporator 49
  • reference numeral 86 denotes a steam drum level control valve that adjusts the water level in the steam drum 72.
  • jacket cooling water is used as it is as the heat transfer water in the exhaust heat recovery path 7 '. That is, the jacket cooling water flowing out from the cylinder jacket 2 flows to the first air cooler (third exhaust heat recovery device) 5. The jacket cooling water heated by cooling the compressed air with the first air cooler 5 evaporates the organic fluid with the evaporator 30 and then returns to the jacket cooling water pump 12.
  • the preheater 1 (see FIG. 1) for exchanging heat with the jacket cooling water can be omitted.
  • a simplified structure can be realized.
  • the jacket cooling water recovered from the first air cooler 5 is directly guided to the evaporator 30 without passing through another heat medium, the recovered heat can be guided to the evaporator 30 with a small heat loss.
  • a heat medium circulation path 8 is provided between the exhaust heat recovery path 7 and the organic fluid path 9.
  • the heat medium circulation path 8 is a closed circuit, and a heat medium circulation pump 11 for circulating the heat medium is provided.
  • the heat medium circulation pump 11 the heat medium circulates through the exhaust heat recovery heat exchanger 13 and the evaporator 30.
  • heat exchange is performed so as to recover heat from the heat transfer medium in the exhaust heat recovery path 7.
  • heat medium oil having a boiling point higher than that of the heat medium water in the exhaust heat recovery path 7 is used.
  • Barretherm registered trademark
  • Matsumura Oil Co., Ltd. is used as the heat medium oil.
  • the heat transfer water in the heat medium path 7 is not guided to the evaporator 30 as in the first embodiment, but the exhaust heat recovered through the heat medium circulation path 8 is guided to the evaporator 30. Also good. Since water is used in the exhaust heat recovery path 7, it is necessary to pressurize the exhaust heat collection path 7 so that the water does not boil and become steam. Depending on the inlet air temperature of the first air cooler 5, the high pressure specification is required. Become. Therefore, if the heat medium circulation path 8 is provided as in the present embodiment and a heat medium oil having a boiling point higher than that of water is mainly used, the pressure of the heat medium circulation path 8 can be used at atmospheric pressure, and exhaust heat recovery is performed. It can be configured as a low-pressure line separated from the path 7.
  • the exhaust heat recovery path 7 is introduced by introducing the heat medium circulation path 8. It is possible to guide exhaust heat to the organic Rankine cycle power generation device 10 using the low-pressure line of the heating medium circulation path 8 while avoiding the long line.
  • FIG. 5 a heating medium circulation path 8 (see FIG. 5) similar to that in the fifth embodiment is provided between the exhaust heat recovery path 7 ′ and the organic fluid path 9 with respect to the fourth embodiment. Is different. Therefore, the same components as those in the fourth embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • a heat medium circulation path 8 is provided between the exhaust heat recovery path 7 ′ and the organic fluid path 9.
  • the heat medium circulation path 8 is a closed circuit, and a heat medium circulation pump 11 for circulating the heat medium is provided.
  • the heat medium circulation pump 11 the heat medium circulates through the exhaust heat recovery heat exchanger 13 and the evaporator 30.
  • heat exchange is performed so that heat is recovered from the jacket cooling water in the exhaust heat recovery path 7 ′.
  • heat medium flowing through the heat medium circulation path 8 for example, heat medium oil having a boiling point higher than that of the heat medium water in the exhaust heat recovery path 7 is used.
  • Barretherm registered trademark
  • Matsumura Oil Co., Ltd. is used as the heat medium oil.
  • the exhaust heat recovered via the heat medium circulation path 8 is guided to the evaporator 30. May be.
  • the line of the exhaust heat recovery path 7 is avoided from becoming a long distance, and then the low pressure line of the heat medium circulation path 8. A configuration using can be made.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Ocean & Marine Engineering (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention concerne un dispositif de production de puissance à récupération de rejet thermique capable d'utiliser, comme source de chaleur pour un cycle de Rankine à fluide organique, le rejet thermique de l'eau de refroidissement d'un moteur dont le niveau de température est inférieur à celui du gaz d'échappement d'un moteur à combustion interne et dont la valeur utile a été faible par le passé. Le dispositif de production de puissance à récupération de rejet thermique est pourvu : d'un trajet de récupération de rejet thermique (7) récupérant la chaleur de l'eau de refroidissement de la chemise destinée à refroidir une chemise de cylindre (2) d'un moteur diesel, et d'un premier refroidisseur d'air (5) destiné à refroidir l'air comprimé évacué d'un compresseur de suralimentation du moteur diesel ; d'un évaporateur (30) faisant s'évaporer un fluide organique au moyen de la chaleur récupérée par le trajet de récupération de rejet thermique (7) ; d'une turbine de travail (32) entraînée par le fluide organique amené à s'évaporer par l'évaporateur (30) ; d'un générateur d'électricité (38) produisant de l'électricité au moyen d'une rotation délivrée par la turbine de travail (32) ; et d'un condenseur (36) condensant le fluide organique passé à travers la turbine de travail (32).
PCT/JP2011/059806 2010-04-26 2011-04-21 Dispositif de production de puissance à récupération de rejet thermique et navire pourvu dudit dispositif WO2011136118A1 (fr)

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KR1020127024546A KR20120136366A (ko) 2010-04-26 2011-04-21 배열 회수 발전 장치 및 이것을 구비한 선박

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WO2013117296A1 (fr) * 2012-02-11 2013-08-15 Daimler Ag Dispositif de récupération d'énergie dans un flux de chaleur perdue d'un moteur à combustion interne de véhicule pourvu d'un circuit de fluide de travail
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WO2013117296A1 (fr) * 2012-02-11 2013-08-15 Daimler Ag Dispositif de récupération d'énergie dans un flux de chaleur perdue d'un moteur à combustion interne de véhicule pourvu d'un circuit de fluide de travail
CN104106201A (zh) * 2012-02-11 2014-10-15 戴姆勒股份公司 用于在车辆中由内燃机的余热流进行能量回收的具有工作介质回路的装置
CN102797833A (zh) * 2012-08-31 2012-11-28 长城汽车股份有限公司 车辆生热构件用冷却节能装置
CN104487661A (zh) * 2012-10-26 2015-04-01 三菱重工业株式会社 内燃机系统及具备该内燃机系统的船舶以及内燃机系统的运行方法
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EP3354869A4 (fr) * 2015-09-24 2018-10-31 Mitsubishi Heavy Industries, Ltd. Équipement de récupération de chaleur, système de moteur à combustion interne, navire, et procédé de récupération de chaleur
CN110056448A (zh) * 2019-04-23 2019-07-26 东风商用车有限公司 一种egr发动机废热回收系统及其控制方法

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