WO2017002624A1 - Système de génération d'énergie - Google Patents

Système de génération d'énergie Download PDF

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Publication number
WO2017002624A1
WO2017002624A1 PCT/JP2016/067819 JP2016067819W WO2017002624A1 WO 2017002624 A1 WO2017002624 A1 WO 2017002624A1 JP 2016067819 W JP2016067819 W JP 2016067819W WO 2017002624 A1 WO2017002624 A1 WO 2017002624A1
Authority
WO
WIPO (PCT)
Prior art keywords
cooling water
passage
evaporator
working fluid
engine
Prior art date
Application number
PCT/JP2016/067819
Other languages
English (en)
Japanese (ja)
Inventor
晋 福永
Original Assignee
いすゞ自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by いすゞ自動車株式会社 filed Critical いすゞ自動車株式会社
Publication of WO2017002624A1 publication Critical patent/WO2017002624A1/fr

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Classifications

    • 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
    • F01K23/10—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
    • 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
    • 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
    • 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

Definitions

  • the present disclosure relates to a power generation system, and more particularly, to a power generation system having a Rankine cycle in which an evaporator evaporates a working fluid with engine coolant.
  • the Rankine cycle is an evaporator that evaporates the working fluid with a heat source, an expander that expands the working fluid, a condenser that condenses the working fluid with a cooling source, and circulates the working fluid in the circulation channel. Arranged in order of circulatory organs.
  • Patent Document 1 discloses a Rankine cycle in which an evaporator heats a working fluid with engine coolant.
  • the temperature of the cooling water that has passed through the engine is not always the same temperature, but varies depending on the operating conditions of the vehicle. For this reason, when the temperature of the cooling water is low (for example, when the engine is warmed up), the evaporator cannot properly evaporate the working fluid with the cooling water, and the Rankine cycle may not operate.
  • the present disclosure has been made in view of these points, and an object thereof is to appropriately evaporate a working fluid with engine cooling water in a Rankine cycle.
  • an exhaust gas is discharged and an evaporator through which circulating cooling water passes, and an evaporator that evaporates a working fluid having a lower melting point than the cooling water by the cooling water in the circulation flow path.
  • An expander that expands the working fluid, a condenser that condenses the working fluid, a Rankine cycle that is arranged in order of the circulator that circulates the working fluid in the circulation flow path, and the cooling water that has passed through the engine A first cooling water passage that is introduced into the evaporator, a second cooling water passage that is branched from the first cooling water passage and is connected to the first cooling water passage, an exhaust passage for the exhaust, and the second Provided is a power generation system comprising: a heat exchanger provided at a location where the cooling water passage intersects, and recovering the heat of the exhaust gas into the cooling water of the second cooling water passage.
  • the power generation system is provided at a branch point of the first cooling water passage with the second cooling water passage, and adjusts a flow rate of the cooling water flowing from the first cooling water passage to the second cooling water passage.
  • a first flow rate adjusting member may be further provided.
  • the power generation system further includes a control unit that controls the operation of the first flow rate adjusting member, and the control unit controls the first flow rate adjusting member according to an evaporation state of the working fluid in the evaporator. It is good also as operating and adjusting the flow volume of the cooling water which flows into the said 2nd cooling water channel
  • the power generation system adjusts a bypass passage that bypasses the evaporator in the first cooling water passage, a flow rate of cooling water introduced into the evaporator, and a flow rate of cooling water flowing into the bypass passage. And a flow rate adjusting member.
  • the power generation system further includes a control unit that controls the operation of the second flow rate adjustment member, and the control unit operates the second flow rate adjustment member when the engine is warmed up, so that the evaporator
  • the cooling water may be caused to flow through the bypass passage without introducing the cooling water into the bypass passage.
  • the working fluid can be appropriately evaporated by the engine coolant in the Rankine cycle.
  • FIG. 1 is a schematic diagram illustrating an example of a configuration of a power generation system S according to an embodiment of the present disclosure.
  • FIG. 2 is a schematic diagram illustrating a configuration of a power generation system 900 according to a comparative example.
  • FIG. Drawing 1 is a mimetic diagram showing an example of composition of power generation system S concerning one embodiment.
  • the power generation system S is mounted on a vehicle having an engine that is an internal combustion engine.
  • the power generation system S is mounted on a large vehicle such as a truck or a bus.
  • the power generation system S regenerates power by using the waste heat generated in the vehicle by the Rankine cycle.
  • the power generation system S includes an engine 10, an exhaust passage 20, a cooling water passage 30, a Rankine cycle 40, a sensor group 70, and an ECU 80.
  • the engine 10 is an engine including a plurality of cylinders, and is a diesel engine in the present embodiment.
  • the engine 10 generates power by burning and expanding a mixture of fuel and intake air (air) in a cylinder.
  • the intake air is drawn into the cylinders of the engine 10 through an intake passage (not shown). Further, the engine 10 exhausts exhaust gas (exhaust gas) after combustion.
  • the exhaust passage 20 is a passage for exhausting the exhaust discharged from the engine 10 to the outside of the vehicle.
  • the exhaust flow path is indicated by a dashed arrow.
  • a supercharger 22 In the exhaust passage 20, a supercharger 22, an aftertreatment device 23, and a heat exchanger 24 are provided.
  • the supercharger 22 is a device that supercharges intake air sucked into the engine 10 by using exhaust pressure as a power source.
  • the supercharger 22 is, for example, a turbocharger, and includes a turbine provided in the exhaust passage 20 and a compressor provided in the intake passage.
  • the post-processing device 23 is a device that purifies exhaust gas.
  • the post-processing device 23 collects PM in exhaust gas or selectively reduces and purifies NO x in exhaust gas using ammonia (NH 3 ) hydrolyzed from urea water as a reducing agent. To do.
  • NH 3 ammonia
  • the heat exchanger 24 is provided at a location where the exhaust passage 20 and the cooling water passage 30 (specifically, a first bypass passage 31a described later) intersect.
  • the heat exchanger 24 is a device that recovers the heat of the exhaust gas in the exhaust passage 20 into the cooling water in the cooling water passage 30. Thereby, the cooling water flowing through the cooling water passage 30 is warmed.
  • the cooling water passage 30 is a passage for circulating cooling water for cooling the engine 10 in order to prevent the engine 10 from being overheated.
  • the flow path of the cooling water is indicated by solid arrows.
  • the cooling water passage 30 is provided so that the cooling water passes through the engine 10, and the cooling water takes the heat of the engine 10 to lower the temperature of the engine 10.
  • the cooling water warmed after passing through the engine 10 is introduced into the evaporator 43 of the Rankine cycle 40 as a heat source.
  • the cooling water passage 30 includes a first bypass passage 31a, a second bypass passage 31b, a third bypass passage 31c, a radiator 32, a pump 33, a first adjustment valve 34, a second adjustment valve 35, A third adjustment valve 36 is provided.
  • the first bypass passage 31 a is a passage that branches from the downstream side of the engine 10 in the cooling water passage 30 and is connected to the cooling water passage 30 on the upstream side of the evaporator 43.
  • the first bypass passage 31a is configured to pass through the heat exchanger 24 on the way. Thereby, the cooling water flowing through the first bypass passage 31a recovers the heat of the exhaust gas by the heat exchanger 24 and is warmed.
  • the cooling water sent from the first bypass passage 31a to the cooling water passage 30 joins with the cooling water that does not flow through the first bypass passage 31a, whereby the temperature of the cooling water sent to the evaporator 43 rises.
  • the cooling water passage 30 corresponds to the first cooling water passage
  • the first bypass passage 31a corresponds to the second cooling water passage.
  • the second bypass passage 31b is a passage that branches from the upstream of the evaporator 43 of the Rankine cycle 40 in the cooling water passage 30 and bypasses the evaporator 43. For example, when the engine 10 is warmed up, the cooling water is bypassed from the evaporator 43 by the second bypass passage 31b.
  • the third bypass passage 31 c is a passage that branches from the upstream side of the radiator 32 in the cooling water passage 30 and bypasses the radiator 32. For example, when the engine 10 is warmed up, the engine 10 is warmed by the cooling water flowing through the third bypass passage 31c.
  • the radiator 32 dissipates the cooling water whose temperature has increased by passing through the engine 10. Specifically, the radiator 32 lowers the temperature of the cooling water by releasing the heat of the sent cooling water into the atmosphere.
  • a cooling fan may be provided behind the radiator 32 in order to promote heat dissipation of the cooling water.
  • the pump 33 circulates the cooling water in the cooling water passage 30.
  • the pump 33 is provided on the downstream side of the engine 10 and pumps the cooling water.
  • the pump 33 operates by receiving a driving force from the engine 10, for example.
  • the first adjusting valve 34 is a flow rate adjusting member that adjusts the flow rate of the coolant that has passed through the engine 10 to the first bypass passage 31a.
  • the first adjustment valve 34 is provided at a branch point between the cooling water passage 30 and the first bypass passage 31a. Thereby, the flow rate of the cooling water for recovering the heat of the exhaust in the heat exchanger 24 can be adjusted.
  • the second adjustment valve 35 adjusts the flow rate of the cooling water to be sent to the evaporator 43 and the flow rate of the cooling water to be diverted to the second bypass passage 31b.
  • the second adjustment valve 35 is provided at the branch point of the cooling water passage 30 to the second bypass passage 31b.
  • the first adjustment valve 34 corresponds to a first flow rate adjustment member
  • the second adjustment valve 35 corresponds to a second flow rate adjustment member.
  • the third adjustment valve 36 adjusts the flow rate of the cooling water to be sent to the radiator 32 and the flow rate of the cooling water to be diverted to the third bypass passage 31c.
  • the third adjustment valve 36 is provided at the branch point of the cooling water passage 30 to the third bypass passage 31c.
  • Rankine cycle 40 is a power generation cycle that generates electric power using cooling water that has passed through engine 10.
  • the Rankine cycle 40 includes a circulation channel 41, a pump 42, an evaporator 43, an expander 44, and a condenser 45.
  • a pump 42, an evaporator 43, an expander 44, and a condenser 45 are arranged in this order in the circulation flow path 41 to form a closed circuit.
  • the circulation channel 41 is a channel through which the working fluid circulates, and is indicated by a one-dot chain line in FIG.
  • the Rankine cycle 40 of the present embodiment is an organic Rankine cycle in which chlorofluorocarbon, which is a medium having a low boiling point, is circulated as a working fluid.
  • the melting point of the working fluid is lower than the melting point of the cooling water.
  • the working fluid for example, known HFC-245fa and HFC-134a are used.
  • the pump 42 is a circulator that circulates the working fluid in the circulation channel 41.
  • the pump 42 sucks the liquid-phase working fluid and pumps it to the evaporator 43.
  • a centrifugal pump, a gear pump, or the like is used as the pump 42.
  • the evaporator 43 is provided on the downstream side of the pump 42 in the circulation flow path 41 and evaporates the working fluid with cooling water. Specifically, the evaporator 43 heats the working fluid by exchanging heat between the working fluid sent from the pump 42 and the cooling water flowing through the cooling water passage 30. In the present embodiment, the cooling water whose exhaust heat has been recovered by the heat exchanger 24 is introduced into the evaporator 43, so that the working fluid can be heated by the cooling water whose temperature is higher than when passing through the engine 10.
  • the expander 44 is provided on the downstream side of the evaporator 43 in the circulation channel 41, and expands the gas phase working fluid heated by the evaporator 43.
  • the expander 44 generates a rotational driving force by expanding the working fluid.
  • a power generator 44 a is connected to the expander 44.
  • the generator 44a generates electric power by being rotated by the rotational driving force generated by the expander 44.
  • the generated electric power is supplied to, for example, a vehicle battery.
  • the condenser 45 is provided on the downstream side of the expander 44 in the circulation channel 41, and condenses the working fluid expanded by the expander 44. Specifically, the condenser 45 liquefies the working fluid by exchanging heat between the working fluid discharged from the expander 44 and the atmosphere as a cooling source. The liquefied working fluid is supplied to the pump 42.
  • the sensor group 70 has a plurality of sensors and can detect various states relating to the vehicle. For example, the sensor group 70 detects the temperature of the cooling water in the cooling water passage 30. The sensor group 70 may detect the heating state of the working fluid in the evaporator 43.
  • the ECU 80 is an electronic control unit (Electric Control Unit) including a microcomputer having a CPU, a ROM, a RAM, and the like.
  • the ECU 80 controls the operation of each device described above.
  • the ECU 80 has a function of a control unit that controls operations of the first adjustment valve 34, the second adjustment valve 35, and the third adjustment valve 36. Further, the ECU 80 may control the operation of the Rankine cycle 40.
  • the first adjustment valve 34 adjusts the opening and closing of the valve so that a part of the cooling water passing through the engine 10 flows to the first bypass passage 31a. Then, the cooling water that has flowed into the first bypass passage 31 a recovers the heat of the exhaust gas that flows through the exhaust passage 20 by the heat exchanger 24. The cooling water from which the heat has been recovered merges with the cooling water that has not flowed through the first bypass passage 31a at the connection point between the first bypass passage 31a and the cooling water passage 30. Thereby, the cooling water is warmed and becomes higher than the temperature when passing through the engine 10.
  • the cooling water whose temperature has been increased is introduced into the evaporator 43 of the Rankine cycle 40.
  • the Rankine cycle 40 can operate appropriately.
  • the temperature of the cooling water that has passed through the engine 10 is low, the temperature is increased by the heat exchanger 24, so that the evaporator 43 can appropriately heat the working fluid.
  • the Rankine cycle 40 can be started early.
  • the cooling water that has passed through the evaporator 43 is radiated when passing through the radiator 32, or bypasses the radiator 32 through the third bypass passage 31c.
  • the coolant passes through the engine 10, it absorbs heat inside the engine 10 and warms up. Thereafter, the cooling water circulates as described above, and continues to serve as a heat source for heating the working fluid in the evaporator 43.
  • the ECU 80 may control the open / close state of the first adjustment valve 34 in accordance with the heating state of the working fluid in the evaporator 43. For example, when the working fluid is sufficiently heated in the evaporator 43, the ECU 80 changes the open / close state of the first adjustment valve 34 so that the cooling water does not flow into the first bypass passage 31a. Thereby, since cooling water does not collect
  • the ECU 80 may control the second adjustment valve 35 so that the cooling water flows to the second bypass passage 31b without being introduced into the evaporator 43 at the start of warm-up. In such a case, the cooling water that has not been heat-recovered as the working fluid in the evaporator 43 passes through the engine 10, so that the temperature of the engine 10 having a low temperature can be effectively increased. Can be promoted.
  • FIG. 2 is a schematic diagram showing a configuration of a power generation system 900 according to a comparative example.
  • the heat exchanger 24, the first bypass passage 31a, and the first adjustment valve 34 shown in FIG. 1 are not provided. That is, in the comparative example, the cooling water that has passed through the engine 10 is introduced into the evaporator 43 of the Rankine cycle 40 without collecting the heat of the exhaust.
  • the evaporator 43 cannot appropriately heat the working fluid using the cooling water as a heat source, and the Rankine cycle 40 may not operate.
  • the engine 10 is warm when the temperature of the engine 10 is low, the temperature of the cooling water passing through the engine 10 is also low, so the evaporator 43 cannot properly heat the working fluid with the cooling water.
  • the cooling water that has passed through the engine 10 includes the heat exchanger 24 and the first bypass passage 31a so that the heat of the exhaust can be recovered.
  • the temperature of the cooling water rises in order to recover the heat of the exhaust gas.
  • the cooling water whose temperature has risen is introduced into the evaporator 43, so that the evaporator 43 appropriately heats the working fluid using the cooling water as a heat source. it can. As a result, it becomes possible to start the Rankine cycle 40 early.
  • the present invention has an effect that the working fluid can be appropriately evaporated by engine coolant in the Rankine cycle, and is useful for a power generation system and the like.

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

Abstract

L'invention concerne un système de production d'énergie comprenant : un moteur (10) qui évacue un échappement et à travers duquel passe de l'eau de refroidissement en circulation; un cycle de Rankine dans lequel, disposés de manière séquentielle sur un trajet d'écoulement (41) de circulation, se trouvent un évaporateur (43) qui utilise de l'eau de refroidissement pour évaporer un fluide de travail ayant un point d'ébullition inférieur à celui de l'eau de refroidissement, un détendeur (44) qui détend le fluide de travail, un condenseur (45) qui condense le fluide de travail, et une pompe (42) qui amène le fluide de travail à circuler à l'intérieur du trajet d'écoulement (41) de circulation; un passage (30) d'eau de refroidissement qui introduit l'eau de refroidissement qui est passée à travers le moteur (10) dans l'évaporateur (43); un premier passage de dérivation (31a) qui se ramifie à partir du passage (30) d'eau de refroidissement puis se raccorde à ce dernier; et un échangeur de chaleur (24) qui est placé au niveau d'un emplacement où un passage d'échappement (20) destiné à l'échappement et le premier passage de dérivation (31a) se croisent, et qui récupère la chaleur de l'échappement pour la transférer à l'eau de refroidissement dans le premier passage de dérivation (31a).
PCT/JP2016/067819 2015-06-30 2016-06-15 Système de génération d'énergie WO2017002624A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-130701 2015-06-30
JP2015130701A JP2017014949A (ja) 2015-06-30 2015-06-30 発電システム

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WO2017002624A1 true WO2017002624A1 (fr) 2017-01-05

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6831318B2 (ja) * 2017-11-22 2021-02-17 株式会社神戸製鋼所 熱エネルギー回収システム
FR3091898B1 (fr) * 2019-01-23 2021-04-09 Ifp Energies Now Circuit de refroidissement d’un moteur thermique equipe d’un circuit recuperateur de chaleur

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008126697A1 (fr) * 2007-04-05 2008-10-23 Calsonic Kansei Corporation Système à cycle de rankine
WO2013046885A1 (fr) * 2011-09-30 2013-04-04 日産自動車株式会社 Cycle de rankine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008126697A1 (fr) * 2007-04-05 2008-10-23 Calsonic Kansei Corporation Système à cycle de rankine
WO2013046885A1 (fr) * 2011-09-30 2013-04-04 日産自動車株式会社 Cycle de rankine

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