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WO2011089997A1 - Dispositif de production d'énergie à récupération de chaleur perdue et navire équipé de ce dernier - Google Patents

Dispositif de production d'énergie à récupération de chaleur perdue et navire équipé de ce dernier Download PDF

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Publication number
WO2011089997A1
WO2011089997A1 PCT/JP2011/050652 JP2011050652W WO2011089997A1 WO 2011089997 A1 WO2011089997 A1 WO 2011089997A1 JP 2011050652 W JP2011050652 W JP 2011050652W WO 2011089997 A1 WO2011089997 A1 WO 2011089997A1
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WIPO (PCT)
Prior art keywords
heat recovery
exhaust heat
exhaust
heat
organic fluid
Prior art date
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Ceased
Application number
PCT/JP2011/050652
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English (en)
Japanese (ja)
Inventor
雅幸 川見
芳弘 市来
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to CN2011800057305A priority Critical patent/CN102713167A/zh
Publication of WO2011089997A1 publication Critical patent/WO2011089997A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • 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
    • 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
    • F01K23/10—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 with exhaust fluid of one cycle heating the fluid in another cycle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/32—Arrangements of propulsion power-unit exhaust uptakes; Funnels peculiar to vessels
    • 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
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/02—Adaptations for driving vehicles, e.g. locomotives
    • F01D15/04—Adaptations for driving vehicles, e.g. locomotives the vehicles being waterborne vessels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • 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
    • 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
    • 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
    • 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
    • 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 generation apparatus that generates power by an organic Rankine cycle using exhaust heat from a diesel generator as a heat source.
  • An object of the present invention is to provide an exhaust heat recovery power generator and a ship equipped with the same.
  • the exhaust heat recovery power generation apparatus of the present invention and a ship equipped with the same adopt the following means. That is, the exhaust heat recovery power generator according to the first aspect of the present invention includes an exhaust heat recovery device that recovers heat by exchanging heat between a heat medium having a boiling point higher than that of water and exhaust heat of an internal combustion engine, and the heat medium.
  • An evaporator that evaporates the organic fluid by exchanging heat with the organic fluid
  • a turbine driven by the organic fluid evaporated by the evaporator
  • a generator that generates electric power by the rotational output of the turbine
  • a turbine And a condenser for condensing the organic fluid that has passed through.
  • 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.
  • an organic Rankine cycle is performed.
  • the exhaust heat of the internal combustion engine is recovered by a heat medium having a boiling point higher than that of water, and the organic fluid is evaporated by the heat medium.
  • the exhaust heat of the internal combustion engine is not recovered by water, but is recovered by using a heat medium having a boiling point higher than that of water.
  • the pressure does not increase as in the case of water. Therefore, it is not necessary to make the heat medium path a high-pressure specification, and it can be configured at a low cost.
  • 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.
  • exhaust heat of an internal combustion engine exhaust gas is typically used. Further, exhaust heat from an air cooler for cooling the compressed air of a supercharger provided in the internal combustion engine, or in the case of a water-cooled internal combustion engine, exhaust heat of engine cooling water can be used.
  • the exhaust heat of the exhaust gas, the air cooler, and the engine cooling water may be used alone or in combination as appropriate, such as exhaust gas and an air cooler.
  • a heating medium oil is preferable.
  • Barreltherm which is a synthetic high boiling point high temperature heating medium oil available from Matsumura Oil Co., Ltd. Is used.
  • the barrel thermo 400 has a boiling point of 390 ° C.
  • the exhaust heat recovery device is provided in the internal combustion engine, a first exhaust heat recovery device that recovers heat from the exhaust gas exhausted from the internal combustion engine.
  • a second exhaust heat recovery unit that recovers heat from an air cooler that cools the compressed air of the supercharger, and / or a third exhaust heat recovery unit that recovers heat from engine cooling water that cools the internal combustion engine are preferably provided.
  • An exhaust heat recovery unit was provided. As a result, a large amount of exhaust heat can be recovered from the internal combustion engine, and the power generation efficiency can be increased.
  • the timing for performing heat recovery by the exhaust heat recovery device can be switched.
  • the evaporator, the turbine, the generator, and the condenser are housed in the same casing.
  • the exhaust heat recovery power generator can be configured compactly. Further, even if the heat medium or the organic fluid leaks out, the outflow of the heat medium or the organic fluid can be stopped in the housing, so that a highly safe exhaust heat recovery power generator can be provided.
  • the ship according to the second aspect of the present invention is provided with the above-described exhaust heat recovery power generation device.
  • exhaust heat is recovered using a heat medium having a boiling point higher than that of water, so that the pressure does not increase as in water even when the exhaust heat of the internal combustion engine becomes high temperature. Therefore, it is not necessary to set the heat medium path to a high-pressure specification, and the exhaust heat recovery power generator can be configured at low cost.
  • FIG. 1 schematically shows a fluid path of the exhaust heat recovery power generator according to this embodiment.
  • the exhaust heat recovery apparatus 10 will be described as a configuration in which the exhaust heat recovery apparatus 10 is installed as exhaust heat recovery for a marine propulsion main engine (diesel engine).
  • the exhaust heat recovery device 10 recovers heat from a first exhaust heat recovery device 1 that is an exhaust gas economizer that recovers heat from exhaust gas discharged from a diesel engine, and an air cooler 3 of a supercharger provided in the diesel engine.
  • the second exhaust heat recovery unit 5 the heat medium path 7 through which the heat medium that receives the exhaust heat from the exhaust heat recovery units 1 and 5 circulates, receives heat from the heat medium in the heat medium path 7, and receives the organic Rankine cycle (Organic And an organic fluid path 9 constituting a Rankine Cycle).
  • the extraction pipe 15 is provided in the flue 13 through which the exhaust gas discharged from the diesel engine flows.
  • the exhaust gas extracted from the extraction pipe 15 flows into the exhaust gas introduction pipe 17 of the exhaust heat recovery power generation apparatus 10.
  • the exhaust gas introduction pipe 17 is provided with a first exhaust gas control valve 18.
  • the exhaust gas guided by the exhaust gas introduction pipe 17 is supplied to the first exhaust heat recovery device 1.
  • the exhaust gas temperature supplied to the first exhaust heat recovery device 1 is, for example, about 230 ° C.
  • An exhaust gas exhaust pipe 19 is connected to the first exhaust heat recovery device 1.
  • the exhaust gas discharge pipe 19 is provided with a second exhaust gas control valve 20.
  • the exhaust gas temperature after heat exchange in the first exhaust heat recovery device 1 is, for example, about 150 ° C.
  • the exhaust gas after heat exchange passes through the exhaust gas discharge pipe 19, returns to the flue 13 through the exhaust gas return pipe 21 connected to the flue 13, and then is discharged from the chimney 23 to the atmosphere.
  • An exhaust gas bypass pipe 25 having an exhaust gas bypass control valve 27 is provided between the exhaust gas introduction pipe 17 and the exhaust gas discharge pipe 19.
  • the opening degrees of the first exhaust gas control valve 18, the second exhaust gas control valve 20 and the exhaust gas bypass control valve 27 the amount of heat recovered by the first exhaust heat recovery device 1 is controlled. Specifically, the temperature, pressure, flow rate, etc. of the exhaust gas entering and exiting the first exhaust heat recovery unit 1 are detected by a sensor (not shown), and the control valves 18, 20, 27 are opened so that the desired heat recovery amount is obtained. Control the degree.
  • the first exhaust heat control valve 18 and the second exhaust gas control valve 20 are closed and the exhaust gas bypass control valve 27 is opened. The exhaust gas supply to the collector 1 is stopped.
  • the air cooler 3 provided in the turbocharger of the diesel engine is used for removing the compression heat of the air compressed by the supercharger.
  • a first heat transfer pipe 34 through which cooling water flows and a second heat transfer pipe 36 through which cooling water flows are provided in order from the low temperature side (from the lower side in FIG. 1). ing.
  • fresh water or seawater used in a cooling system in the ship is used as the cooling water guided to the first heat transfer pipe 34 and the second heat transfer pipe 36.
  • the temperature of the air supplied from the supercharger to the air cooler 3 is, for example, about 170 ° C.
  • the temperature of the air that has finished heat exchange in the air cooler 3 is, for example, about 30 ° C.
  • the cooling water for exhaust heat recovery that introduces the cooling water whose heat exchange is completed in the second heat transfer pipe 36 to the second exhaust heat recovery unit 5 is introduced.
  • the temperature of the cooling water flowing into the second exhaust heat recovery unit 5 is, for example, about 150 ° C.
  • the temperature of the cooling water after the heat exchange in the second exhaust heat recovery unit 5 is, for example, 120 ° C.
  • the first cooling water valve 42 is provided in the cooling water introduction pipe 38 for exhaust heat recovery.
  • the upstream end of the cooling water return pipe 44 is connected to the upstream side of the first cooling water valve 42.
  • the cooling water that has passed through the cooling water return pipe 44 is returned to the cooling water return line.
  • the cooling water return pipe 44 is provided with a second cooling water valve 45.
  • the cooling water discharge pipe 40 for exhaust heat recovery is provided with a cooling water circulation pump P2 and a third cooling water valve 47. Cooling water is circulated between the second exhaust heat recovery device 5 and the third heat transfer pipe 36 by the cooling water circulation pump P2.
  • connection pipe 49 One end of a connection pipe 49 is connected to the downstream side of the third cooling water valve 47.
  • the other end of the connection pipe 49 is connected to the second heat transfer pipe cooling water introduction pipe 53.
  • the connection pipe 49 is provided with a fourth cooling water valve 51.
  • the downstream end of the second heat transfer pipe cooling water introduction pipe 53 is connected to a midway position of the cooling water return pipe 44 located downstream of the second cooling water valve 45.
  • the second heat transfer tube cooling water introduction pipe 53 is provided with a fifth cooling water valve 55.
  • the first to fifth cooling water valves 42, 45, 47, 51, 55 operate as follows.
  • the first cooling water valve 42 and the third cooling water valve 47 are opened, and the second exhaust heat recovery unit 5 and the second heat transfer pipe 36 are opened. Circulate cooling water.
  • the second cooling water valve 45 and the fourth cooling water valve 51 are closed, the fifth cooling water valve 55 is opened, and the cooling water introduced from the first heat transfer pipe 34 is introduced into the second heat transfer pipe cooling water. It passes through the pipe 53, passes through the fifth cooling water valve 55, passes through the cooling water return pipe 44, and is returned to the cooling water return line.
  • the first cooling water valve 42 and the third cooling water valve 47 are closed. Then, the second cooling water valve 45 and the fourth cooling water valve 51 are opened, and the fifth cooling water valve 55 is closed. Thereby, the cooling water led from the first heat transfer pipe 34 passes through the second heat transfer pipe cooling water introduction pipe 53 and the connection pipe 49 and is led to the second heat transfer pipe 36, and then the exhaust heat recovery cooling water. It flows through the introduction pipe 38 and the cooling water return pipe 44 to the cooling water return line.
  • heat medium path 7 As the heat medium flowing through the heat medium path 7, a heat medium having a boiling point higher than that of water is used, and heat medium oil is preferably used. Specifically, Barrel Therm (registered trademark), which is a heat medium oil for synthetic high boiling point and high temperature available from Matsumura Oil Co., Ltd., is used.
  • the barrel thermo 400 has a boiling point of 390 ° C.
  • the heat medium path 7 is a closed circuit, and a heat medium circulation pump P1 for circulating the heat medium is provided.
  • a heat medium circulation pump P1 for circulating the heat medium is provided.
  • the heat medium is circulated so as to exchange heat with the first exhaust heat recovery device 1, the evaporator 60, and the second exhaust heat recovery device 5.
  • the heat medium inlet temperature of the evaporator 60 is, for example, about 210 ° C., and the heat medium outlet temperature is, for example, about 100 ° C.
  • the organic fluid is evaporated by the heat medium.
  • the inlet temperature of the organic fluid in the evaporator 60 is, for example, about 90 ° C., and the outlet temperature is, for example, about 200 ° C.
  • 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 circulation pump P0 for circulating the organic fluid is provided.
  • the organic fluid circulates while repeating the phase change so as to pass through the evaporator 60, the power turbine 62, the preheater 64, and the condenser 66.
  • the power turbine 62 is rotationally driven by a heat drop (enthalpy drop) of the organic fluid evaporated by the evaporator 60.
  • the rotational power of the power turbine 62 is transmitted to the generator 68, and electric power is obtained by the generator 68.
  • the electric power obtained by the generator 68 is supplied to the inboard system via a power line (not shown).
  • the organic fluid (gas phase) that has finished the work in the power turbine 68 preheats the organic fluid (liquid phase) sent from the organic fluid circulation pump P0 by the preheater 64.
  • the organic fluid that has passed through the preheater 64 is cooled by seawater in the condenser 66 to be condensed and liquefied.
  • the condensed and liquefied organic fluid is sent to the preheater 64 and the evaporator 60 by the organic fluid circulation pump P0.
  • the organic fluid path 9 constitutes an organic Rankine cycle together with the evaporator 60, the power turbine 62, the preheater 64, and the condenser 66.
  • FIG. 2 shows an arrangement example of a main part of the exhaust heat recovery power generator 10 shown in FIG.
  • each device is accommodated in the housing 11.
  • the inside of the housing 11 is a closed space.
  • all of the heat medium circulation pump P 1, a part of the heat medium path 7 connected to the heat medium circulation pump P 1, and the organic fluid path 9 are evaporated.
  • a vessel 60, a power turbine 62, a generator 68, a preheater 64, a condenser 66, and an organic fluid circulation pump P0 are provided.
  • the principal part of an exhaust-heat recovery electric power generation apparatus can be unitized. Thereby, it can be made compact and the installation property to an existing ship etc. can be improved.
  • a ventilation fan 70 is provided on the upper surface of the housing 11 so that the heat medium and the organic fluid flowing into the housing 11 can be discharged to the outside.
  • the operation of the exhaust heat recovery power generation apparatus 10 having the above configuration will be described with reference to FIG.
  • a part of the exhaust gas from the diesel engine is extracted and guided to the first exhaust heat recovery unit 1.
  • the heat medium circulating in the heat medium path 7 and the exhaust gas are heat-exchanged, and the sensible heat of the exhaust gas is recovered in the heat medium.
  • the air compressed by the supercharger is cooled by the second heat transfer tube 36 of the air cooler 3.
  • the cooling water flowing in the second heat transfer tube 36 is heated by the air to recover heat from the air.
  • the cooling water heated by the second heat transfer tube 36 is guided to the second exhaust heat recovery device 5.
  • the heat medium circulating in the heat medium path 7 and the cooling water are heat-exchanged, and the sensible heat of the cooling water is recovered to the heat medium.
  • the exhaust heat is recovered by the second exhaust heat recovery device 5 and the exhaust heat is recovered by the first exhaust heat recovery device 1, and the heat medium that has reached a high temperature is led to the evaporator 60 and passes through the organic fluid path 9. Exchanges heat with circulating organic fluid.
  • the organic fluid is heated and evaporated by the sensible heat of the heat medium in the evaporator 60.
  • the organic fluid that has evaporated to high enthalpy is guided to the power turbine 62, and the power turbine 62 is driven to rotate by the heat drop. Rotational output of the power turbine 62 is obtained, and power generation is performed by the generator 68.
  • the organic fluid (gas phase) that has finished work in the power turbine 62 is preheated to the organic fluid (liquid phase) before flowing into the evaporator 60 by the pre-heater 64, and then led to the condenser 66, It is condensed and liquefied when cooled.
  • the first exhaust heat recovery device 1 can be operated without exhaust heat recovery. Further, by switching the cooling water valves 42, 45, 47, 51, 55, the second exhaust heat recovery unit 5 can be operated without recovering the exhaust heat. Thus, since the timing of the heat recovery by the first exhaust heat recovery device 1 or the second exhaust heat recovery device 5 can be switched, whether or not the exhaust heat recovery is necessary according to the operating state of the diesel engine, the onboard power demand, etc. Can be decided. Thereby, a highly flexible power generation system can be constructed.
  • the exhaust heat is recovered by the first exhaust heat recovery device 1 and the second exhaust heat recovery device 5, but as shown in FIG.
  • the exhaust heat recovery may be omitted and only the exhaust heat recovery from the exhaust gas using the first exhaust heat recovery device 1 may be performed.
  • the exhaust heat recovery from the exhaust gas of the diesel engine may be omitted, and only the exhaust heat recovery from the supercharger using the second exhaust heat recovery device 5 may be performed.
  • the air cooler is divided into a first air cooler 3a and a second air cooler 3b, and the second exhaust heat is supplied from the first air cooler 3a located on the upstream side of the air flow.
  • a configuration in which exhaust heat recovery is performed by the recovery unit 5 may be adopted. With such a configuration, the cooling water circulation pump P2 is driven only when exhaust heat recovery is performed, and the cooling water circulation pump P2 is stopped when exhaust heat recovery is not performed. Thereby, each cooling water valve 42, 45, 47, 51, 55 shown in FIG. 1 is omissible.
  • the first air cooler 3a can be independently designed as a heat exchanger having a capacity necessary for operating the organic Rankine cycle.
  • the above-described exhaust heat recovery power generation apparatus 10 of the present embodiment has been described by way of example as applied to a ship.
  • the present invention is not limited to this, and may be applied to, for example, a land-use internal combustion engine used for power generation or the like. it can.
  • exhaust heat from engine cooling water can be used as the third exhaust heat recovery unit.
  • the third exhaust heat recovery unit may be used in combination with the first exhaust heat recovery unit 1 and the second exhaust heat recovery unit 5, or the second exhaust heat recovery unit 5 in FIG.
  • Three exhaust heat recovery devices may be used. Or it replaces with the 2nd waste heat recovery device 5 of Drawing 4, and a 3rd waste heat recovery device can also be used independently.

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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

Un dispositif de production d'énergie à récupération de chaleur perdue comprend : des dispositifs de récupération de chaleur perdue (1, 5) destinés à récupérer la chaleur par la réalisation d'un échange de chaleur entre un moteur à combustion interne et un milieu chauffant ayant un point d'ébullition supérieur à celui de l'eau ; un vaporisateur (60) destiné à vaporiser un fluide organique par la réalisation d'un échange de chaleur entre le milieu chauffant et le fluide organique ; une turbine de puissance (62) entraînée par le fluide organique qui est vaporisé par le vaporisateur (60) ; un générateur (68) destiné à générer de l'électricité par la sortie rotative de la turbine de puissance (62) ; un dispositif de préchauffage (64) destiné à préchauffer le fluide organique qui circule dans l'évaporateur, le préchauffage étant effectué par le fluide organique ayant traversé la turbine de puissance (62) ; et un condenseur (66) destiné à condenser le fluide organique.
PCT/JP2011/050652 2010-01-21 2011-01-17 Dispositif de production d'énergie à récupération de chaleur perdue et navire équipé de ce dernier Ceased WO2011089997A1 (fr)

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CN103017132A (zh) * 2013-01-06 2013-04-03 徐海军 电热蒸汽锅炉系统
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US10047638B2 (en) 2015-04-09 2018-08-14 Kobe Steel, Ltd. Heat energy recovery system
EP3093456A1 (fr) * 2015-04-09 2016-11-16 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Système de récupération d'énergie thermique
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US11274629B2 (en) 2016-12-05 2022-03-15 Orean Energy AG System and method for energy recovery in industrial faciliiies
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JP2019007379A (ja) * 2017-06-22 2019-01-17 株式会社神戸製鋼所 熱エネルギー回収システム及びそれを搭載する船舶
EP3569829A1 (fr) * 2018-04-18 2019-11-20 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Dispositif de récupération d'énergie thermique et procédé d'installation d'un dispositif de récupération d'énergie thermique
CN112260316A (zh) * 2020-10-20 2021-01-22 浙江大学 一种离网型多能互补的冷热电湿联供系统及其方法
CN112260316B (zh) * 2020-10-20 2022-05-03 浙江大学 一种离网型多能互补的冷热电湿联供系统及其方法
IT202200014326A1 (it) * 2022-07-06 2024-01-06 Sondag Energy Srl Impianto solare termodinamico per generare vapore ad alta temperatura per la produzione di energia elettrica

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