JP2021008873A - Heat cycle system - Google Patents

Heat cycle system Download PDF

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JP2021008873A
JP2021008873A JP2019124285A JP2019124285A JP2021008873A JP 2021008873 A JP2021008873 A JP 2021008873A JP 2019124285 A JP2019124285 A JP 2019124285A JP 2019124285 A JP2019124285 A JP 2019124285A JP 2021008873 A JP2021008873 A JP 2021008873A
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organic medium
heat
heat exchanger
temperature
flow path
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JP7096212B2 (en
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恵三 岩間
Keizo Iwama
恵三 岩間
孝裕 小島
Takahiro Kojima
孝裕 小島
土佐　真一
Shinichi Tosa
真一 土佐
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Honda Motor Co Ltd
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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/61—Types of temperature control
    • H01M10/613—Cooling or keeping cold
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L58/00—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles
    • B60L58/10—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries
    • B60L58/24—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries for controlling the temperature of batteries
    • B60L58/26—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries for controlling the temperature of batteries by cooling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L58/00—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles
    • B60L58/10—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries
    • B60L58/24—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries for controlling the temperature of batteries
    • B60L58/27—Methods or circuit arrangements for monitoring or controlling batteries or fuel cells, specially adapted for electric vehicles for monitoring or controlling batteries for controlling the temperature of batteries by heating
    • 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
    • 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
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • 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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/61—Types of temperature control
    • H01M10/615—Heating or keeping warm
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/62—Heating or cooling; Temperature control specially adapted for specific applications
    • H01M10/625—Vehicles
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/63—Control systems
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/65—Means for temperature control structurally associated with the cells
    • H01M10/655—Solid structures for heat exchange or heat conduction
    • H01M10/6556—Solid parts with flow channel passages or pipes for heat exchange
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/65—Means for temperature control structurally associated with the cells
    • H01M10/656—Means for temperature control structurally associated with the cells characterised by the type of heat-exchange fluid
    • H01M10/6567—Liquids
    • H01M10/6568—Liquids characterised by flow circuits, e.g. loops, located externally to the cells or cell casings
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/65—Means for temperature control structurally associated with the cells
    • H01M10/656—Means for temperature control structurally associated with the cells characterised by the type of heat-exchange fluid
    • H01M10/6569—Fluids undergoing a liquid-gas phase change or transition, e.g. evaporation or condensation
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries
    • 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
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/70—Energy storage systems for electromobility, e.g. batteries

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Electrochemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Power Engineering (AREA)
  • Transportation (AREA)
  • Automation & Control Theory (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

To provide a heat cycle system which enables recovery of exhaust heat of an engine and temperature control of a battery to be performed efficiently.SOLUTION: A rankine cycle circuit 5 includes: a main circulation passage 50 in which an organic medium circulates; a condenser 52; an evaporator 56; a compression expander 51; an electronic expansion valve 54; and a battery 81 enabling heat exchange with the organic medium in a battery container 55 in the main circulation passage 50. A control device 7 operates the rankine cycle circuit 5 so that the organic medium circulates through the evaporator 56, the compression expander 51, and the condenser 52 in this order in an engine cooling mode and a hybrid cooling mode, and operates the rankine cycle circuit 5 so that the organic medium circulates through the compression expander 51, the battery container 55, the electronic expansion valve 54, and the condenser 52 in this order in a battery warming mode.SELECTED DRAWING: Figure 3A

Description

本発明は、熱サイクルシステムに関する。より詳しくは、内燃機関の冷却回路と、ランキンサイクル回路と、を備える熱サイクルシステムに関する。 The present invention relates to a thermal cycle system. More specifically, the present invention relates to a thermal cycle system including a cooling circuit of an internal combustion engine and a Rankine cycle circuit.

近年、ランキンサイクルを利用して、車両の内燃機関の廃熱から機械エネルギや電気エネルギを取り出す廃熱回収システムの開発が進められている。このような廃熱回生システムにおいて、廃熱からエネルギを取り出すランキンサイクルは、作動媒体を圧送するポンプと、作動媒体を内燃機関の廃熱で加熱する熱交換器と、熱交換器によって加熱された作動媒体を膨張させることにより機械エネルギや電気エネルギを発生する膨張機と、膨張機によって膨張された作動媒体を凝縮させるコンデンサと、を備えるランキンサイクル回路によって実現される（例えば、特許文献１参照）。 In recent years, the development of a waste heat recovery system that extracts mechanical energy and electrical energy from the waste heat of an internal combustion engine of a vehicle by using the Rankine cycle has been promoted. In such a waste heat regeneration system, the Rankine cycle that extracts energy from waste heat is heated by a pump that pumps the working medium, a heat exchanger that heats the working medium with the waste heat of the internal combustion engine, and a heat exchanger. It is realized by a Rankine cycle circuit including an expander that generates mechanical energy or electrical energy by expanding the working medium and a capacitor that condenses the working medium expanded by the expander (see, for example, Patent Document 1). ..

特開２００６−１１８７５４号公報Japanese Unexamined Patent Publication No. 2006-118754

ところで駆動力発生源として内燃機関の他、電動機を備える所謂ハイブリッド車両には、電動機に電力を供給するバッテリを好ましい温度に維持するバッテリ温調システムが搭載される。しかしながらこのようなバッテリ温調システムを上述の廃熱回収システムと別に構築しようとすると、バッテリを加温するヒータやバッテリを冷却する冷却回路等が必要になり、車両全体の部品点数、重量、及びコスト等が増加するおそれがある。 By the way, in addition to an internal combustion engine as a driving force generation source, a so-called hybrid vehicle equipped with an electric motor is equipped with a battery temperature control system that maintains a battery that supplies electric power to the electric motor at a preferable temperature. However, if such a battery temperature control system is to be constructed separately from the above-mentioned waste heat recovery system, a heater for heating the battery, a cooling circuit for cooling the battery, etc. are required, and the number of parts, weight, and the number of parts of the entire vehicle are increased. There is a risk that costs will increase.

本発明は、内燃機関の廃熱回収とバッテリの温調との両方を行うことができる熱サイクルシステムを提供することを目的とする。 An object of the present invention is to provide a thermal cycle system capable of both recovering waste heat of an internal combustion engine and controlling the temperature of a battery.

（１）本発明に係る熱サイクルシステム（例えば、後述の熱サイクルシステム１）は、内燃機関（例えば、後述のエンジン２）及びその排気と熱交換を行う冷却水が循環する冷却回路（例えば、後述の冷却回路３）と、絶縁性の有機媒体が循環する循環流路（例えば、後述の主循環流路５０）、前記循環流路に設けられ有機媒体と外気との間で熱交換を行う第１熱交換器（例えば、後述の凝縮器５２）、前記循環流路に設けられ有機媒体と冷却水との間で熱交換を行う第２熱交換器（例えば、後述の蒸発器５６）、前記循環流路に設けられ前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮し、前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する圧縮膨張機（例えば、後述の圧縮膨張機５１）、及び前記圧縮膨張機に接続されたモータジェネレータ（例えば、後述のモータジェネレータ５７）を備えるランキンサイクル回路（例えば、後述のランキンサイクル回路５）と、前記内燃機関又は当該内燃機関と相関のある部分の温度である内燃機関温度が所定の廃熱回収可能温度より高い場合には、前記第２熱交換器、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作する制御装置（例えば、後述の制御装置７）と、を備え、前記ランキンサイクル回路は、前記循環流路に設けられ前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する膨張弁（例えば、後述の電子膨張弁５４）と、前記循環流路内の熱交換部（例えば、後述のバッテリ容器５５）において有機媒体と熱交換が可能な蓄電装置（例えば、後述のバッテリ８１）と、を備え、前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が加温要求状態である場合には、前記圧縮膨張機、前記熱交換部、前記膨張弁、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することを特徴とする。 (1) The heat cycle system according to the present invention (for example, the heat cycle system 1 described later) is a cooling circuit (for example, a cooling circuit in which cooling water that exchanges heat with the internal combustion engine (for example, the engine 2 described later) and its exhaust is circulated. A cooling circuit 3) described later, a circulation flow path in which an insulating organic medium circulates (for example, a main circulation flow path 50 described later), and heat exchange between the organic medium and the outside air provided in the circulation flow path. A first heat exchanger (for example, a condenser 52 described later), a second heat exchanger provided in the circulation flow path for heat exchange between an organic medium and cooling water (for example, an evaporator 56 described later). The organic medium provided in the circulation flow path and flowing from the first heat exchanger side to the second heat exchanger side is compressed, and the organic medium flowing from the second heat exchanger side to the first heat exchanger side is compressed. A Rankin cycle circuit (for example, a Rankin cycle circuit 5 described later) including a compression expander for depressurizing (for example, a compression expander 51 described later) and a motor generator connected to the compression expander (for example, a motor generator 57 described later). ), And when the internal combustion engine temperature, which is the temperature of the internal combustion engine or a portion correlated with the internal combustion engine, is higher than the predetermined waste heat recoverable temperature, the second heat exchanger, the compression expander, and the said. A control device (for example, a control device 7 described later) that operates the Rankin cycle circuit so that the organic medium circulates in the order of the first heat exchanger is provided, and the Rankin cycle circuit is provided in the circulation flow path. An expansion valve (for example, an electronic expansion valve 54 described later) for reducing the pressure of the organic medium flowing from the second heat exchanger side to the first heat exchanger side, and a heat exchange unit (for example, described later) in the circulation flow path. The battery container 55) includes a power storage device (for example, a battery 81 described later) capable of heat exchange with an organic medium, and the control device has the internal combustion engine temperature equal to or lower than the waste heat recoverable temperature and said. When the power storage device is in a heating request state, the Rankin cycle circuit is operated so that the organic medium circulates in the order of the compression expander, the heat exchange unit, the expansion valve, and the first heat exchanger. It is characterized by doing.

（２）この場合、前記循環流路には、前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮するポンプ（例えば、後述の第１ポンプ５３）が前記膨張弁と並列になるように設けられ、前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が冷却要求状態である場合には、前記ポンプ、前記熱交換部、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することが好ましい。 (2) In this case, in the circulation flow path, a pump (for example, the first pump 53 described later) that compresses the organic medium flowing from the first heat exchanger side to the second heat exchanger side is the expansion valve. When the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a cooling required state, the control device is provided with the pump, the heat exchange unit, and the like. It is preferable to operate the Rankine cycle circuit so that the organic medium circulates in the order of the compression expander and the first heat exchanger.

（３）本発明に係る熱サイクルシステム（例えば、後述の熱サイクルシステム１）は、内燃機関（例えば、後述のエンジン２）及びその排気と熱交換を行う冷却水が循環する冷却回路（例えば、後述の冷却回路３）と、絶縁性の有機媒体が循環する循環流路（例えば、後述の主循環流路５０）、前記循環流路に設けられ有機媒体と外気との間で熱交換を行う第１熱交換器（例えば、後述の凝縮器５２）、前記循環流路に設けられ有機媒体と冷却水との間で熱交換を行う第２熱交換器（例えば、後述の蒸発器５６）、前記循環流路に設けられ前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮し、前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する圧縮膨張機（例えば、後述の圧縮膨張機５１）、及び前記圧縮膨張機に接続されたモータジェネレータ（例えば、後述のモータジェネレータ５７）を備えるランキンサイクル回路（例えば、後述のランキンサイクル回路５）と、前記内燃機関又は当該内燃機関と相関のある部分の温度である内燃機関温度が所定の廃熱回収可能温度より高い場合には、前記第２熱交換器、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作する制御装置（例えば、後述の制御装置７）と、を備え、前記ランキンサイクル回路は、前記循環流路に設けられ前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮するポンプ（例えば、後述の第１ポンプ５３）と、前記循環流路内の熱交換部において有機媒体と熱交換が可能な蓄電装置（例えば、後述のバッテリ８１）と、を備え、前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が冷却要求状態である場合には、前記ポンプ、前記熱交換部、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することを特徴とする。 (3) The heat cycle system according to the present invention (for example, the heat cycle system 1 described later) is a cooling circuit (for example, a cooling circuit in which cooling water that exchanges heat with the internal combustion engine (for example, the engine 2 described later) and its exhaust is circulated. A cooling circuit 3) described later, a circulation flow path in which an insulating organic medium circulates (for example, a main circulation flow path 50 described later), and heat exchange between the organic medium and the outside air provided in the circulation flow path. A first heat exchanger (for example, a condenser 52 described later), a second heat exchanger provided in the circulation flow path for heat exchange between an organic medium and cooling water (for example, an evaporator 56 described later). The organic medium provided in the circulation flow path and flowing from the first heat exchanger side to the second heat exchanger side is compressed, and the organic medium flowing from the second heat exchanger side to the first heat exchanger side is compressed. A Rankin cycle circuit (for example, a Rankin cycle circuit 5 described later) including a compression expander for depressurizing (for example, a compression expander 51 described later) and a motor generator connected to the compression expander (for example, a motor generator 57 described later). ), And when the internal combustion engine temperature, which is the temperature of the internal combustion engine or a portion correlated with the internal combustion engine, is higher than the predetermined waste heat recoverable temperature, the second heat exchanger, the compression expander, and the said. A control device (for example, a control device 7 described later) that operates the Rankin cycle circuit so that the organic medium circulates in the order of the first heat exchanger is provided, and the Rankin cycle circuit is provided in the circulation flow path. A pump that compresses the organic medium flowing from the first heat exchanger side to the second heat exchanger side (for example, the first pump 53 described later) and the heat exchange section in the circulation flow path generate heat with the organic medium. A replaceable power storage device (for example, a battery 81 described later) is provided, and the control device is used when the internal combustion engine temperature is equal to or lower than the waste heat recovery temperature and the power storage device is in a cooling request state. Is characterized in that the Rankin cycle circuit is operated so that the organic medium circulates in the order of the pump, the heat exchange unit, the compression expander, and the first heat exchanger.

（４）この場合、前記循環流路には、前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する膨張弁（例えば、後述の電子膨張弁５４）が前記ポンプと並列になるように設けられ、前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が加温要求状態である場合には、前記圧縮膨張機、前記熱交換部、前記膨張弁、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することが好ましい。 (4) In this case, an expansion valve (for example, an electronic expansion valve 54 described later) for reducing the pressure of the organic medium flowing from the second heat exchanger side to the first heat exchanger side is pumped in the circulation flow path. When the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a heating request state, the control device is provided with the compression expander and the heat. It is preferable to operate the Rankine cycle circuit so that the organic medium circulates in the order of the switching part, the expansion valve, and the first heat exchanger.

（５）この場合、前記循環流路には、第１の流れ方向に沿って順に、前記ポンプと、前記熱交換部と、前記第２熱交換器と、前記圧縮膨張機と、前記第１熱交換器と、が設けられ、前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が前記冷却要求状態である場合には、前記熱交換部における有機媒体が沸騰した状態で維持されるように、前記ポンプ及び前記モータジェネレータを操作することが好ましい。 (5) In this case, in the circulation flow path, the pump, the heat exchange unit, the second heat exchanger, the compression expander, and the first one are in order along the first flow direction. A heat exchanger is provided, and when the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in the cooling required state, the organic medium in the heat exchange unit is provided. It is preferable to operate the pump and the motor generator so that the heat is maintained in a boiling state.

（６）この場合、前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が前記冷却要求状態である場合には、前記熱交換部における有機媒体の沸点が前記蓄電装置の目標温度で維持されるように、前記ポンプ及び前記モータジェネレータを用いて前記熱交換部における有機媒体の量及び圧力を制御することが好ましい。 (6) In this case, in this case, when the internal combustion engine temperature is equal to or lower than the waste heat recovery temperature and the power storage device is in the cooling required state, the boiling point of the organic medium in the heat exchange unit is high. It is preferable to control the amount and pressure of the organic medium in the heat exchange section by using the pump and the motor generator so as to maintain the target temperature of the power storage device.

（１）本発明の熱サイクルシステムにおいて、制御装置は、内燃機関温度が廃熱回収可能温度より高く、内燃機関の廃熱によってモータジェネレータで発電させることができる場合には、第２熱交換器、圧縮膨張機、及び第１熱交換器の順で有機媒体が循環するようにランキンサイクル回路を操作する。このように有機媒体を循環させると、有機媒体は、第２熱交換器において内燃機関及びその排気によって加温された冷却水によって加温され、圧縮膨張機において減圧され、第１熱交換器において外気との熱交換によって冷却される。これにより内燃機関温度が廃熱回収可能温度より高い場合には、内燃機関の廃熱の一部を、圧縮膨張機において有機媒体を減圧する過程で、モータジェネレータによって電気エネルギとして回収できる。また本発明において、ランキンサイクル回路は、循環流路において第２熱交換器側から第１熱交換器側へ流れる有機媒体を減圧する膨張弁と、循環流路内の熱交換部において有機媒体と熱交換が可能な蓄電装置と、を備える。また制御装置は、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が加温要求状態である場合には、圧縮膨張機、熱交換部、膨張弁、及び第１熱交換器の順で有機媒体が循環するようにランキンサイクル回路を操作する。このように有機媒体を循環させると、有機媒体は、圧縮膨張機において圧縮され、熱交換部において蓄電装置との熱交換によって冷却され、膨張弁によって減圧され、第１熱交換器において外気との熱交換によって加温される。これにより内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が加温要求状態である場合には、外気の熱エネルギの一部を蓄電装置に与えることにより、蓄電装置を加温できる。以上より本発明の熱サイクルシステムによれば、内燃機関の廃熱回収と蓄電装置の加温との両方を行うことができる。 (1) In the heat cycle system of the present invention, the control device is a second heat exchanger when the temperature of the internal combustion engine is higher than the waste heat recoverable temperature and the waste heat of the internal combustion engine can generate electricity with the motor generator. The Rankine cycle circuit is operated so that the organic medium circulates in the order of, compression expander, and first heat exchanger. When the organic medium is circulated in this way, the organic medium is heated in the second heat exchanger by the cooling water heated by the internal combustion engine and its exhaust, depressurized in the compression expander, and in the first heat exchanger. It is cooled by heat exchange with the outside air. As a result, when the internal combustion engine temperature is higher than the waste heat recoverable temperature, a part of the waste heat of the internal combustion engine can be recovered as electric energy by the motor generator in the process of depressurizing the organic medium in the compression expander. Further, in the present invention, the Rankine cycle circuit includes an expansion valve that reduces the pressure of the organic medium flowing from the second heat exchanger side to the first heat exchanger side in the circulation flow path, and an organic medium in the heat exchange section in the circulation flow path. It is equipped with a power storage device capable of heat exchange. When the internal combustion engine temperature is below the waste heat recovery temperature and the power storage device is in a heating request state, the control device is in the order of the compression expander, the heat exchange unit, the expansion valve, and the first heat exchanger. Operate the Rankine cycle circuit so that the organic medium circulates in. When the organic medium is circulated in this way, the organic medium is compressed in the compression expander, cooled by heat exchange with the power storage device in the heat exchange section, depressurized by the expansion valve, and with the outside air in the first heat exchanger. It is heated by heat exchange. As a result, when the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a heating required state, the power storage device can be heated by giving a part of the heat energy of the outside air to the power storage device. From the above, according to the heat cycle system of the present invention, both waste heat recovery of the internal combustion engine and heating of the power storage device can be performed.

（２）本発明では、循環流路には、上述のように第２熱交換器側から第１熱交換器側へ流れる有機媒体を減圧する膨張弁と、これとは逆に第１熱交換器側から第２熱交換器側へ流れる有機媒体を圧縮するポンプとを並列に設ける。また制御装置は、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、ポンプ、熱交換部、圧縮膨張機、及び第１熱交換器の順で有機媒体が循環するようにランキンサイクル回路を操作する。このように有機媒体を循環させると、有機媒体は、ポンプによって圧縮され、熱交換部において蓄電装置との熱交換によって加温され、圧縮膨張機において減圧され、第１熱交換器において外気との熱交換によって冷却される。これにより内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、蓄電装置の熱エネルギの一部を外気に放出することにより、蓄電装置を冷却できる。以上より本発明の熱サイクルシステムによれば、内燃機関の廃熱回収と、蓄電装置の加温及び冷却とを行うことができる。 (2) In the present invention, the circulation flow path has an expansion valve for reducing the pressure of the organic medium flowing from the second heat exchanger side to the first heat exchanger side as described above, and conversely, the first heat exchange. A pump for compressing the organic medium flowing from the vessel side to the second heat exchanger side is provided in parallel. When the internal combustion engine temperature is lower than the waste heat recovery temperature and the power storage device is in the cooling required state, the control device is organic in the order of the pump, the heat exchanger, the compression expander, and the first heat exchanger. Operate the Rankine cycle circuit so that the medium circulates. When the organic medium is circulated in this way, the organic medium is compressed by the pump, heated by heat exchange with the power storage device in the heat exchange section, depressurized in the compression expander, and with the outside air in the first heat exchanger. It is cooled by heat exchange. As a result, when the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in the cooling required state, the power storage device can be cooled by releasing a part of the thermal energy of the power storage device to the outside air. From the above, according to the heat cycle system of the present invention, waste heat recovery of the internal combustion engine and heating and cooling of the power storage device can be performed.

（３）本発明の熱サイクルシステムでは、上記（１）の発明と同様の手順により、内燃機関の廃熱の一部を、圧縮膨張機において有機媒体を減圧する過程で、モータジェネレータによって電気エネルギとして回収できる。また本発明において、ランキンサイクル回路は、循環流路において第１熱交換器側から第２熱交換器側へ流れる有機媒体を圧縮するポンプと、循環流路内の熱交換部において有機媒体と熱交換が可能な蓄電装置と、を備える。また制御装置は、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、ポンプ、熱交換部、圧縮膨張機、及び第１熱交換器の順で有機媒体が循環するようにランキンサイクル回路を操作する。このように有機媒体を循環させると、有機媒体は、ポンプによって圧縮され、熱交換部において蓄電装置との熱交換によって加温され、圧縮膨張機において減圧され、第１熱交換器において外気との熱交換によって冷却される。これにより内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、蓄電装置の熱エネルギの一部を外気に放出することにより、蓄電装置を冷却できる。以上より本発明の熱サイクルシステムによれば、内燃機関の廃熱回収と、蓄電装置の冷却との両方を行うことができる。 (3) In the thermal cycle system of the present invention, a part of the waste heat of the internal combustion engine is decompressed by the motor generator in the process of decompressing the organic medium in the compression expander by the same procedure as the invention of the above (1). Can be collected as. Further, in the present invention, the Rankine cycle circuit includes a pump that compresses an organic medium flowing from the first heat exchanger side to the second heat exchanger side in the circulation flow path, and heat with the organic medium in the heat exchange section in the circulation flow path. It is equipped with a replaceable power storage device. When the internal combustion engine temperature is lower than the waste heat recovery temperature and the power storage device is in the cooling required state, the control device is organic in the order of the pump, the heat exchanger, the compression expander, and the first heat exchanger. Operate the Rankine cycle circuit so that the medium circulates. When the organic medium is circulated in this way, the organic medium is compressed by the pump, heated by heat exchange with the power storage device in the heat exchange section, depressurized in the compression expander, and with the outside air in the first heat exchanger. It is cooled by heat exchange. As a result, when the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in the cooling required state, the power storage device can be cooled by releasing a part of the thermal energy of the power storage device to the outside air. From the above, according to the heat cycle system of the present invention, both waste heat recovery of the internal combustion engine and cooling of the power storage device can be performed.

（４）本発明では、循環流路には、上述のように第１熱交換器側から第２熱交換器側へ流れる有機媒体を圧縮するポンプと、これとは逆に第２熱交換器側から第１熱交換器側へ流れる有機媒体を減圧する膨張弁とを並列に設ける。また制御装置は、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が加温要求状態である場合には、圧縮膨張機、熱交換部、膨張弁、及び第１熱交換器の順で有機媒体が循環するようにランキンサイクル回路を操作する。このように有機媒体を循環させると、有機媒体は、圧縮膨張機において圧縮され、熱交換部において蓄電装置との熱交換によって冷却され、膨張弁によって減圧され、第１熱交換器において外気との熱交換によって加温される。これにより内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が加温要求状態である場合には、外気の熱エネルギの一部を蓄電装置に与えることにより、蓄電装置を加温できる。以上より本発明の熱サイクルシステムによれば、内燃機関の廃熱回収と蓄電装置の加温及び冷却とを行うことができる。 (4) In the present invention, the circulation flow path includes a pump that compresses the organic medium flowing from the first heat exchanger side to the second heat exchanger side as described above, and a second heat exchanger conversely. An expansion valve for reducing the pressure of the organic medium flowing from the side to the first heat exchanger side is provided in parallel. When the internal combustion engine temperature is below the waste heat recovery temperature and the power storage device is in a heating request state, the control device is in the order of the compression expander, the heat exchange unit, the expansion valve, and the first heat exchanger. Operate the Rankine cycle circuit so that the organic medium circulates in. When the organic medium is circulated in this way, the organic medium is compressed in the compression expander, cooled by heat exchange with the power storage device in the heat exchange section, depressurized by the expansion valve, and with the outside air in the first heat exchanger. It is heated by heat exchange. As a result, when the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a heating required state, the power storage device can be heated by giving a part of the heat energy of the outside air to the power storage device. From the above, according to the heat cycle system of the present invention, waste heat recovery of the internal combustion engine and heating and cooling of the power storage device can be performed.

（５）本発明において、制御装置は、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、蓄電装置との間で熱交換が可能な熱交換部において有機媒体が沸騰した状態で維持されるようにポンプ及びモータジェネレータを操作する。本発明によれば、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、熱交換部において蓄電装置を有機媒体の潜熱によって冷却できるので、蓄電装置を効果的に冷却できる。 (5) In the present invention, the control device is a heat exchange unit capable of exchanging heat with the power storage device when the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a cooling required state. The pump and motor generator are operated so that the organic medium is kept in a boiling state. According to the present invention, when the temperature of the internal combustion engine is equal to or lower than the waste heat recoverable temperature and the power storage device is in a cooling required state, the power storage device can be cooled by the latent heat of the organic medium in the heat exchange unit. Can be cooled effectively.

（６）本発明において、制御装置は、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、熱交換部における有機媒体の沸点が蓄電装置の目標温度で維持されるように、ポンプ及びモータジェネレータを用いて熱交換部における有機媒体の量及び圧力を制御する。本発明によれば、内燃機関温度が廃熱回収可能温度以下でありかつ蓄電装置が冷却要求状態である場合には、熱交換部において蓄電装置を有機媒体の潜熱によって冷却しながら、この有機媒体の温度を蓄電装置の目標温度で維持できるので、蓄電装置を速やかに目標温度まで低下させることができる。 (6) In the present invention, in the control device, when the internal temperature of the internal combustion engine is equal to or lower than the waste heat recovery temperature and the power storage device is in the cooling required state, the boiling point of the organic medium in the heat exchange unit is the target temperature of the power storage device. A pump and a motor generator are used to control the amount and pressure of the organic medium in the heat exchange section so that it is maintained at. According to the present invention, when the temperature of the internal combustion engine is equal to or lower than the waste heat recoverable temperature and the power storage device is in a cooling required state, the power storage device is cooled by the latent heat of the organic medium in the heat exchange unit, and the organic medium is cooled. Since the temperature can be maintained at the target temperature of the power storage device, the power storage device can be quickly lowered to the target temperature.

本発明の一実施形態に係る熱サイクルシステムの構成を示す図である。It is a figure which shows the structure of the thermal cycle system which concerns on one Embodiment of this invention. 制御装置によって実現される複数の制御モードの内容を説明するための表である。It is a table for demonstrating the contents of a plurality of control modes realized by a control device. バッテリ加温モードで実現される有機媒体の流れを示す図である。It is a figure which shows the flow of the organic medium realized in the battery heating mode. バッテリ冷却モードで実現される有機媒体の流れを示す図である。It is a figure which shows the flow of the organic medium realized in the battery cooling mode. 第１及び第２エンジン冷却モードで実現される有機媒体の流れを示す図である。It is a figure which shows the flow of the organic medium realized in the 1st and 2nd engine cooling modes. 第１及び第２ハイブリッド冷却モードで実現される有機媒体の流れを示す図である。It is a figure which shows the flow of the organic medium realized in the 1st and 2nd hybrid cooling modes. バッテリ加温モードの実行時にランキンサイクル回路において実現される熱サイクルのモリエル線図である。It is a Moriel diagram of the thermal cycle realized in the Rankine cycle circuit when the battery heating mode is executed. バッテリ冷却モードの実行時にランキンサイクル回路において実現される熱サイクルのモリエル線図である。It is a Moriel diagram of the thermal cycle realized in the Rankine cycle circuit when the battery cooling mode is executed. 第１及び第２エンジン冷却モードの実行時にランキンサイクル回路において実現される熱サイクルのモリエル線図である。FIG. 5 is a Moriel diagram of the thermal cycle realized in the Rankine cycle circuit when the first and second engine cooling modes are executed. 第１及び第２ハイブリッド冷却モードの実行時にランキンサイクル回路において実現される熱サイクルのモリエル線図である。FIG. 5 is a Moriel diagram of the thermal cycle realized in the Rankine cycle circuit when the first and second hybrid cooling modes are executed.

以下、本発明の一実施形態について、図面を参照しながら説明する。
図１は、本実施形態に係る熱サイクルシステム１の構成を示す図である。熱サイクルシステム１は、内燃機関２（以下、「エンジン２」という）を備える車両に搭載され、始動時におけるエンジン２を暖機したり、暖機後のエンジン２で生じる廃熱を回収し電気エネルギに変換したりする。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a diagram showing a configuration of a thermal cycle system 1 according to the present embodiment. The thermal cycle system 1 is mounted on a vehicle equipped with an internal combustion engine 2 (hereinafter referred to as "engine 2") to warm up the engine 2 at the time of starting and to recover waste heat generated in the engine 2 after warming up to generate electricity. Convert to energy.

熱サイクルシステム１は、エンジン２をその経路の一部に含み冷却水が循環する冷却回路３と、絶縁性の有機媒体が循環するランキンサイクル回路５と、これら冷却回路３及びランキンサイクル回路５を操作する制御装置７と、放電及び充電が可能なバッテリ８１と、を備える。 The thermal cycle system 1 includes a cooling circuit 3 in which the engine 2 is included in a part of the path and circulation of cooling water, a Rankine cycle circuit 5 in which an insulating organic medium circulates, and these cooling circuits 3 and the Rankine cycle circuit 5. A control device 7 to be operated and a battery 81 capable of discharging and charging are provided.

冷却回路３は、エンジン２及びその排気と熱交換を行う冷却水が循環する冷却水の循環流路３３と、この循環流路３３に設けられた複数の装置によって構成される。より具体的には、冷却回路３は、ランキンサイクル回路５に設けられる後述の蒸発器５６を流路に含む循環流路３３と、この循環流路３３の一部である第１冷却水流路３１と、循環流路３３の一部である第２冷却水流路３２と、循環流路３３において冷却水を圧送する第１ウォータポンプ３５及び第２ウォータポンプ３６と、循環流路３３を流れる冷却水によってキャビンを加温するヒータコア３７と、循環流路３３のうち第２冷却水流路３２、第２ウォータポンプ３６、及びヒータコア３７を迂回するバイパス流路３４と、を備える。 The cooling circuit 3 is composed of a cooling water circulation flow path 33 through which cooling water that exchanges heat with the engine 2 and its exhaust gas circulates, and a plurality of devices provided in the circulation flow path 33. More specifically, the cooling circuit 3 includes a circulation flow path 33 including an evaporator 56, which will be described later, provided in the Rankin cycle circuit 5, and a first cooling water flow path 31 which is a part of the circulation flow path 33. The second cooling water flow path 32, which is a part of the circulation flow path 33, the first water pump 35 and the second water pump 36 for pumping the cooling water in the circulation flow path 33, and the cooling water flowing through the circulation flow path 33. A heater core 37 that heats the cabin and a bypass flow path 34 that bypasses the second cooling water flow path 32, the second water pump 36, and the heater core 37 among the circulation flow paths 33 are provided.

第１冷却水流路３１は、エンジン２のシリンダブロックに形成された冷却水の流路であり、冷却水とエンジン２との間の熱交換を促進する。第２冷却水流路３２は、冷却水と排気との間の熱交換を促進する冷却水の流路である。この第２冷却水流路３２は、排気管のうち排気浄化触媒２１よりも下流側に形成される。蒸発器５６は、環状の循環流路３３において、第１ウォータポンプ３５及び第２ウォータポンプ３６で冷却水を循環させた場合に第２冷却水流路３２及びヒータコア３７より下流側でありかつ第１冷却水流路３１より上流側であるような位置に設けられる。 The first cooling water flow path 31 is a flow path for cooling water formed in the cylinder block of the engine 2 and promotes heat exchange between the cooling water and the engine 2. The second cooling water flow path 32 is a flow path for cooling water that promotes heat exchange between the cooling water and the exhaust gas. The second cooling water flow path 32 is formed in the exhaust pipe on the downstream side of the exhaust purification catalyst 21. The evaporator 56 is on the downstream side of the second cooling water flow path 32 and the heater core 37 and is the first in the annular circulation flow path 33 when the cooling water is circulated by the first water pump 35 and the second water pump 36. It is provided at a position such that it is on the upstream side of the cooling water flow path 31.

第１ウォータポンプ３５は、循環流路３３のうち蒸発器５６と第１冷却水流路３１との間に設けられる。第１ウォータポンプ３５は、制御装置７からの制御信号に応じて作動し、循環流路３３内において蒸発器５６側から第１冷却水流路３１側へ冷却水を圧送する。 The first water pump 35 is provided between the evaporator 56 and the first cooling water flow path 31 in the circulation flow path 33. The first water pump 35 operates in response to a control signal from the control device 7, and pumps cooling water from the evaporator 56 side to the first cooling water flow path 31 side in the circulation flow path 33.

バイパス流路３４は、循環流路３３のうち、第１冷却水流路３１と第２冷却水流路３２との間の分岐部３８と、蒸発器５６とを接続する。このため第１冷却水流路３１から流出する冷却水の一部は、このバイパス流路３４を介して蒸発器５６又は第１ウォータポンプ３５へ還流される。 The bypass flow path 34 connects the branch portion 38 between the first cooling water flow path 31 and the second cooling water flow path 32 and the evaporator 56 of the circulation flow path 33. Therefore, a part of the cooling water flowing out from the first cooling water flow path 31 is returned to the evaporator 56 or the first water pump 35 via the bypass flow path 34.

第２ウォータポンプ３６は、循環流路３３のうち分岐部３８と第２冷却水流路３２との間に設けられる。第２ウォータポンプ３６は、制御装置７からの制御信号に応じて作動し、循環流路３３内において第１冷却水流路３１側から第２冷却水流路３２側へ冷却水を圧送する。 The second water pump 36 is provided between the branch portion 38 and the second cooling water flow path 32 in the circulation flow path 33. The second water pump 36 operates in response to a control signal from the control device 7, and pumps cooling water from the first cooling water flow path 31 side to the second cooling water flow path 32 side in the circulation flow path 33.

ランキンサイクル回路５は、冷却水より低沸点かつ低比熱でありさらに絶縁性の有機媒体が循環する環状の主循環流路５０と、この主循環流路５０に設けられた圧縮膨張機５１、凝縮器５２、第１ポンプ５３、電子膨張弁５４、バッテリ容器５５、及び蒸発器５６と、主循環流路５０に設けられた複数の装置の一部を迂回するバイパス流路６０と、このバイパス流路６０に設けられた第２ポンプ６１と、を備える。 The Rankine cycle circuit 5 includes an annular main circulation flow path 50 in which an insulating organic medium having a boiling point and a lower specific heat than that of cooling water circulates, a compression expander 51 provided in the main circulation flow path 50, and condensation. A device 52, a first pump 53, an electronic expansion valve 54, a battery container 55, an evaporator 56, a bypass flow path 60 that bypasses a part of a plurality of devices provided in the main circulation flow path 50, and this bypass flow. A second pump 61 provided on the road 60 is provided.

圧縮膨張機５１は、主循環流路５０のうち蒸発器５６と凝縮器５２との間に設けられる。圧縮膨張機５１は、主循環流路５０を蒸発器５６側から凝縮器５２側へ流れる有機媒体を減圧し（以下、この流れ方向を「第１の流れ方向Ｆ１」ともいう）、主循環流路５０を凝縮器５２側から蒸発器５６側へ流れる有機媒体を圧縮する（以下、この流れ方向を「第２の流れ方向Ｆ２」ともいう）。圧縮膨張機５１は、主循環流路５０を有機媒体が第１の流れ方向Ｆ１に沿って流れる正転時には、蒸発器５６を経た有機媒体を減圧して凝縮器５２へ供給する。また圧縮膨張機５１は、主循環流路５０を有機媒体が第２の流れ方向Ｆ２に沿って流れる逆転時には、凝縮器５２を経た有機媒体を圧縮して蒸発器５６へ供給する。 The compression expander 51 is provided between the evaporator 56 and the condenser 52 in the main circulation flow path 50. The compression expander 51 decompresses the organic medium flowing through the main circulation flow path 50 from the evaporator 56 side to the condenser 52 side (hereinafter, this flow direction is also referred to as “first flow direction F1”), and the main circulation flow. The organic medium flowing through the path 50 from the condenser 52 side to the evaporator 56 side is compressed (hereinafter, this flow direction is also referred to as "second flow direction F2"). The compression expander 51 decompresses the organic medium that has passed through the evaporator 56 and supplies it to the condenser 52 when the organic medium flows in the main circulation flow path 50 along the first flow direction F1 in the normal rotation. Further, the compression expander 51 compresses the organic medium that has passed through the condenser 52 and supplies the organic medium to the evaporator 56 at the time of reversal in which the organic medium flows through the main circulation flow path 50 along the second flow direction F2.

また圧縮膨張機５１の駆動軸５１ａには、モータジェネレータ５７が接続されている。このモータジェネレータ５７は、制御装置７からの制御信号に応じて、バッテリ８１との間で電気エネルギの授受が可能となっている。このためモータジェネレータ５７は、バッテリ８１から供給される電力を用いて圧縮膨張機５１を正転又は逆転させたり、圧縮膨張機５１において有機媒体を減圧させる過程で回収した機械エネルギで発電し、この発電電力でバッテリ８１を充電したりすることが可能となっている。 A motor generator 57 is connected to the drive shaft 51a of the compression expander 51. The motor generator 57 can transfer electrical energy to and from the battery 81 in response to a control signal from the control device 7. Therefore, the motor generator 57 uses the electric power supplied from the battery 81 to rotate the compression / expander 51 forward or reverse, or generates electricity with the mechanical energy recovered in the process of depressurizing the organic medium in the compression / expansion machine 51. It is possible to charge the battery 81 with the generated power.

凝縮器５２は、主循環流路５０において第１の流れ方向Ｆ１に沿って圧縮膨張機５１の下流側に設けられる。凝縮器５２は、有機媒体が通流する有機媒体流路と、この有機媒体流路に外気を供給するファンと、を備え、有機媒体と外気との間で熱交換を行う。 The condenser 52 is provided on the downstream side of the compression expander 51 along the first flow direction F1 in the main circulation flow path 50. The condenser 52 includes an organic medium flow path through which the organic medium passes and a fan that supplies outside air to the organic medium flow path, and exchanges heat between the organic medium and the outside air.

蒸発器５６は、主循環流路５０において第１の流れ方向Ｆ１に沿って圧縮膨張機５１の上流側に設けられる。蒸発器５６は、有機媒体が通流する有機媒体流路と、冷却回路３の冷却水が通流する冷却水流路とを備え、有機媒体と冷却水との間で熱交換を行う。 The evaporator 56 is provided on the upstream side of the compression expander 51 along the first flow direction F1 in the main circulation flow path 50. The evaporator 56 includes an organic medium flow path through which the organic medium flows and a cooling water flow path through which the cooling water of the cooling circuit 3 passes, and exchanges heat between the organic medium and the cooling water.

バッテリ容器５５は、主循環流路５０において第１の流れ方向Ｆ１に沿って蒸発器５６の上流側に設けられる。バッテリ容器５５の内部には、有機媒体が通流する。またバッテリ容器５５の内部には、有機媒体に浸漬するようにバッテリ８１が設けられている。このためバッテリ８１は、バッテリ容器５５内を通流する有機媒体との間で熱交換が可能となっている。 The battery container 55 is provided on the upstream side of the evaporator 56 along the first flow direction F1 in the main circulation flow path 50. An organic medium passes through the inside of the battery container 55. Further, inside the battery container 55, a battery 81 is provided so as to be immersed in an organic medium. Therefore, the battery 81 can exchange heat with the organic medium flowing through the battery container 55.

主循環流路５０のうち凝縮器５２とバッテリ容器５５との間の部分は、第１分岐路５０ａと第２分岐路５０ｂとに枝分かれしている。また第１分岐路５０ａには第１ポンプ５３が設けられ、第２分岐路５０ｂには電子膨張弁５４が設けられている。すなわちこれら第１ポンプ５３及び電子膨張弁５４は、主循環流路５０において並列に設けられている。 The portion of the main circulation flow path 50 between the condenser 52 and the battery container 55 is branched into a first branch passage 50a and a second branch passage 50b. A first pump 53 is provided in the first branch passage 50a, and an electronic expansion valve 54 is provided in the second branch passage 50b. That is, the first pump 53 and the electronic expansion valve 54 are provided in parallel in the main circulation flow path 50.

第１ポンプ５３は、第１分岐路５０ａにおいて第１の流れ方向Ｆ１に沿って凝縮器５２の下流側かつバッテリ容器５５の上流側に設けられている。第１ポンプ５３は、制御装置７からの制御信号に応じて作動し、第１分岐路５０ａにおいて第１の流れ方向Ｆ１に沿って流れる有機媒体を圧縮する。第１ポンプ５３の回転数は、制御装置７によって調整される。 The first pump 53 is provided on the downstream side of the condenser 52 and on the upstream side of the battery container 55 along the first flow direction F1 in the first branch path 50a. The first pump 53 operates in response to a control signal from the control device 7 to compress the organic medium flowing along the first flow direction F1 in the first branch path 50a. The rotation speed of the first pump 53 is adjusted by the control device 7.

電子膨張弁５４は、第２分岐路５０ｂにおいて第２の流れ方向Ｆ２に沿ってバッテリ容器５５の下流側かつ凝縮器５２の上流側に設けられている。電子膨張弁５４は、絞り弁であり、第２分岐路５０ｂにおいて第２の流れ方向Ｆ２に沿って流れる有機媒体を減圧する。電子膨張弁５４の開度は、制御装置７からの制御信号に応じて調整される。 The electronic expansion valve 54 is provided on the downstream side of the battery container 55 and on the upstream side of the condenser 52 along the second flow direction F2 in the second branch passage 50b. The electronic expansion valve 54 is a throttle valve and depressurizes the organic medium flowing along the second flow direction F2 in the second branch passage 50b. The opening degree of the electronic expansion valve 54 is adjusted according to the control signal from the control device 7.

以上より、第１の流れ方向Ｆ１に沿った順では、主循環流路５０には、圧縮膨張機５１と、凝縮器５２と、第１ポンプ５３と、バッテリ容器５５と、蒸発器５６と、が設けられている。また第２の流れ方向Ｆ２に沿った順では、主循環流路５０には、圧縮膨張機５１と、蒸発器５６と、バッテリ容器５５と、電子膨張弁５４と、凝縮器５２と、が設けられている。 From the above, in the order along the first flow direction F1, the main circulation flow path 50 includes a compression expander 51, a condenser 52, a first pump 53, a battery container 55, and an evaporator 56. Is provided. Further, in the order along the second flow direction F2, the main circulation flow path 50 is provided with a compression expander 51, an evaporator 56, a battery container 55, an electronic expansion valve 54, and a condenser 52. Has been done.

バイパス流路６０は、主循環流路５０のうち凝縮器５２及び分岐路５０ａ，５０ｂの間と、バッテリ容器５５及び蒸発器５６の間とを接続する。すなわちバイパス流路６０は、主循環流路５０において第１ポンプ５３、電子膨張弁５４、及びバッテリ容器５５を迂回する流路を形成する。 The bypass flow path 60 connects between the condenser 52 and the branch paths 50a and 50b of the main circulation flow path 50 and between the battery container 55 and the evaporator 56. That is, the bypass flow path 60 forms a flow path that bypasses the first pump 53, the electronic expansion valve 54, and the battery container 55 in the main circulation flow path 50.

第２ポンプ６１は、制御装置７からの制御信号に応じて作動し、主循環流路５０において第１の流れ方向Ｆ１に沿って流れる有機媒体を圧縮する。第２ポンプ６１の回転数は、制御装置７によって調整される。すなわちこの第２ポンプ６１をオンにすることにより、凝縮器５２から第１の流れ方向Ｆ１に沿って流出する有機媒体の一部を第１ポンプ５３、電子膨張弁５４、及びバッテリ容器５５から迂回して蒸発器５６へ還流させる。 The second pump 61 operates in response to a control signal from the control device 7 to compress the organic medium flowing along the first flow direction F1 in the main circulation flow path 50. The rotation speed of the second pump 61 is adjusted by the control device 7. That is, by turning on the second pump 61, a part of the organic medium flowing out from the condenser 52 along the first flow direction F1 is bypassed from the first pump 53, the electronic expansion valve 54, and the battery container 55. Then, it is refluxed to the evaporator 56.

以上のような熱サイクルシステム１によれば、制御装置７によってランキンサイクル回路５の第１ポンプ５３、電子膨張弁５４、モータジェネレータ５７、及び第２ポンプ６１等を操作することにより、複数の制御モードでランキンサイクル回路５を作動させることができる。 According to the thermal cycle system 1 as described above, a plurality of controls are performed by operating the first pump 53, the electronic expansion valve 54, the motor generator 57, the second pump 61, and the like of the Rankine cycle circuit 5 by the control device 7. The Rankine cycle circuit 5 can be operated in the mode.

図２は、制御装置７によって実現される複数の制御モードの内容をまとめた表である。
図２に示すように、制御モードは、主にバッテリ８１を加温するバッテリ加温モードと、主にバッテリ８１を冷却するバッテリ冷却モードと、エンジン２の廃熱を回収しながらエンジン２及びその冷却水を冷却する第１エンジン冷却モードと、エンジン２の廃熱を回収しながらバッテリ８１とエンジン２及びその冷却水を冷却する第１ハイブリッド冷却モードと、第１エンジン冷却モードよりも速やかにエンジン２を冷却する第２エンジン冷却モードと、第１ハイブリッド冷却モードよりも速やかにバッテリ８１とエンジン２及びその冷却水とを冷却する第２ハイブリッド冷却モードと、の６つに分けられる。なお上記６つの制御モードのうち、バッテリ冷却モード、第１エンジン冷却モード、及び第１ハイブリッド冷却モードは、バッテリ８１やエンジン２の廃熱を回収できる廃熱回収モードであるともいえる。 FIG. 2 is a table summarizing the contents of a plurality of control modes realized by the control device 7.
As shown in FIG. 2, the control modes are a battery heating mode that mainly heats the battery 81, a battery cooling mode that mainly cools the battery 81, and the engine 2 and the engine 2 while recovering the waste heat of the engine 2. The first engine cooling mode that cools the cooling water, the first hybrid cooling mode that cools the battery 81, the engine 2 and its cooling water while recovering the waste heat of the engine 2, and the engine faster than the first engine cooling mode. It is divided into six modes: a second engine cooling mode for cooling 2 and a second hybrid cooling mode for cooling the battery 81, the engine 2 and its cooling water more quickly than the first hybrid cooling mode. Of the above six control modes, the battery cooling mode, the first engine cooling mode, and the first hybrid cooling mode can be said to be waste heat recovery modes capable of recovering the waste heat of the battery 81 and the engine 2.

図２に示すように、制御装置７は、エンジン２の状態を、エンジン２の冷却水温度に応じて３つの状態に分ける。より具体的には、エンジン２の状態は、冷却水温度が所定の廃熱回収可能温度よりも低くランキンサイクル回路５でエンジン２の廃熱を回収できない廃熱回収不可状態と、冷却水温度が上記廃熱回収可能温度以上でありランキンサイクル回路５でエンジン２の廃熱を回収できる廃熱回収可能状態と、冷却水温度が上記廃熱回収可能温度より高く設定されたエンジン保護温度以上でありエンジン２及びその冷却水を速やかに冷却する必要があるエンジン保護要求状態と、に分けられる。なお以下では、エンジン２の状態を、エンジン２と相関のある部分の温度であるエンジン２の冷却水の温度によって廃熱回収不可状態と、廃熱回収可能状態と、エンジン保護要求状態とに分類する場合について説明するが、本発明はこれに限らない。より具体的には、エンジン２の冷却水温度の代わりにエンジン２の温度によってエンジン２の状態を分類してもよい。 As shown in FIG. 2, the control device 7 divides the state of the engine 2 into three states according to the cooling water temperature of the engine 2. More specifically, the state of the engine 2 is that the cooling water temperature is lower than the predetermined waste heat recoverable temperature and the waste heat of the engine 2 cannot be recovered by the Rankin cycle circuit 5, and the cooling water temperature is different. The waste heat recoverable temperature is equal to or higher than the waste heat recoverable temperature, and the waste heat recoverable state of the engine 2 can be recovered by the Rankin cycle circuit 5, and the cooling water temperature is higher than the waste heat recoverable temperature set to be higher than the engine protection temperature. It is divided into an engine protection request state in which the engine 2 and its cooling water need to be cooled promptly. In the following, the state of the engine 2 is classified into a state in which waste heat cannot be recovered, a state in which waste heat can be recovered, and a state in which engine protection is required, depending on the temperature of the cooling water of the engine 2, which is the temperature of the portion correlated with the engine 2. However, the present invention is not limited to this. More specifically, the state of the engine 2 may be classified according to the temperature of the engine 2 instead of the cooling water temperature of the engine 2.

また図２に示すように、制御装置７は、バッテリ８１の状態を、その温度であるバッテリ温度に応じて２つの状態に分ける。より具体的には、バッテリ８１の状態は、バッテリ温度がその最適温度より低くバッテリ８１を加温する必要があるバッテリ加温要求状態と、バッテリ温度が上記最適温度以上でありバッテリ８１を冷却する必要があるバッテリ冷却要求状態と、に分けられる。 Further, as shown in FIG. 2, the control device 7 divides the state of the battery 81 into two states according to the battery temperature, which is the temperature thereof. More specifically, the states of the battery 81 include a battery heating request state in which the battery temperature is lower than the optimum temperature and the battery 81 needs to be heated, and a battery temperature is equal to or higher than the optimum temperature to cool the battery 81. It is divided into the required battery cooling requirements and the required battery cooling conditions.

図２に示すように、制御装置７は、エンジン２の状態が廃熱回収不可状態でありかつバッテリ８１の状態がバッテリ加温要求状態である場合には、バッテリ加温モードの下でランキンサイクル回路５を操作し、エンジン２の状態が廃熱回収不可状態でありかつバッテリ８１の状態がバッテリ冷却要求状態である場合には、バッテリ冷却モードの下でランキンサイクル回路５を操作する。また制御装置７は、エンジン２の状態が廃熱回収可能状態でありかつバッテリ８１の状態がバッテリ加温要求状態である場合には、第１エンジン冷却モードの下でランキンサイクル回路５を操作し、エンジン２の状態が廃熱回収可能状態でありかつバッテリ８１の状態がバッテリ冷却要求状態である場合には、第１ハイブリッド冷却モードの下でランキンサイクル回路５を操作する。また制御装置７は、エンジン２の状態がエンジン保護要求状態でありかつバッテリ８１の状態がバッテリ加温要求状態である場合には、第２エンジン冷却モードの下でランキンサイクル回路５を操作し、エンジン２の状態がエンジン保護要求状態でありかつバッテリ８１の状態がバッテリ冷却要求状態である場合には、第２ハイブリッド冷却モードの下でランキンサイクル回路５を操作する。以下、各制御モードの詳細について説明する。 As shown in FIG. 2, when the state of the engine 2 is the state where the waste heat cannot be recovered and the state of the battery 81 is the battery heating request state, the control device 7 is a Rankine cycle under the battery heating mode. When the circuit 5 is operated and the state of the engine 2 is the state where waste heat recovery is not possible and the state of the battery 81 is the battery cooling request state, the Rankine cycle circuit 5 is operated under the battery cooling mode. Further, the control device 7 operates the Rankine cycle circuit 5 under the first engine cooling mode when the state of the engine 2 is the state in which waste heat can be recovered and the state of the battery 81 is the state requiring battery heating. When the state of the engine 2 is the state in which waste heat can be recovered and the state of the battery 81 is the state requiring battery cooling, the Rankine cycle circuit 5 is operated under the first hybrid cooling mode. Further, when the state of the engine 2 is the engine protection request state and the state of the battery 81 is the battery heating request state, the control device 7 operates the Rankin cycle circuit 5 under the second engine cooling mode. When the state of the engine 2 is the engine protection required state and the state of the battery 81 is the battery cooling required state, the Rankin cycle circuit 5 is operated under the second hybrid cooling mode. The details of each control mode will be described below.

＜バッテリ加温モード＞
図３Ａは、バッテリ加温モードの実行時にランキンサイクル回路５において実現される有機媒体の流れを示す図である。制御装置７は、バッテリ加温モードでは、図３Ａにおいて太矢印で示すように、有機媒体が第２の流れ方向Ｆ２に沿って、圧縮膨張機５１、蒸発器５６、バッテリ容器５５、電子膨張弁５４、及び凝縮器５２の順で循環するようにランキンサイクル回路５を操作する。より具体的には、制御装置７は、バッテリ加温モードでは、第１ポンプ５３及び第２ポンプ６１をオフにするとともに、バッテリ８１からモータジェネレータ５７に電力を供給することによってモータジェネレータ５７で圧縮膨張機５１を逆転させ、さらに電子膨張弁５４を開く。バッテリ加温モードでは、制御装置７によって上述のようにランキンサイクル回路５を操作することによって、図４Ａに示すような熱サイクルが実現される。 <Battery heating mode>
FIG. 3A is a diagram showing the flow of the organic medium realized in the Rankine cycle circuit 5 when the battery heating mode is executed. In the battery heating mode, the control device 7 has a compression expander 51, an evaporator 56, a battery container 55, and an electronic expansion valve along the second flow direction F2, as shown by a thick arrow in FIG. 3A. The Rankine cycle circuit 5 is operated so as to circulate in the order of 54 and the condenser 52. More specifically, in the battery heating mode, the control device 7 turns off the first pump 53 and the second pump 61, and compresses the motor generator 57 by supplying electric power from the battery 81 to the motor generator 57. The expander 51 is reversed, and the electronic expansion valve 54 is further opened. In the battery heating mode, the control device 7 operates the Rankine cycle circuit 5 as described above to realize the thermal cycle as shown in FIG. 4A.

図４Ａは、バッテリ加温モードの実行時にランキンサイクル回路５において実現される熱サイクルを示すモリエル線図である。図４Ａには、有機媒体の飽和蒸気線を細破線で示し、有機媒体の飽和液線を細一点鎖線で示す。すなわち、有機媒体は、飽和蒸気線より右側では過熱蒸気の状態となり、飽和液線より左側では過冷却液の状態となり、飽和蒸気線と飽和液線との間では沸騰した状態となる。図４Ａに示すように、バッテリ加温モードの実行時には、有機媒体は、圧縮膨張機５１によって圧縮され、過熱蒸気の状態で蒸発器５６及びバッテリ容器５５に供給される。圧縮膨張機５１によって圧縮された有機媒体は、蒸発器５６及びバッテリ容器５５を流れる過程で冷却水及びバッテリ８１との熱交換によって冷却され、過冷却液の状態で電子膨張弁５４に供給される。電子膨張弁５４に供給された有機媒体は、電子膨張弁５４によって減圧され、過冷却液の状態又は混相状態で凝縮器５２に供給される。電子膨張弁５４から供給された有機媒体は、凝縮器５２を流れる過程で外気との熱交換によって加熱され、過熱蒸気の状態で圧縮膨張機５１に供給される。このため、バッテリ加温モードの実行時には、外気の熱エネルギの一部がバッテリ８１に供給されるため、これによりバッテリ８１の温度が上昇する。 FIG. 4A is a Moriel diagram showing the thermal cycle realized in the Rankine cycle circuit 5 when the battery heating mode is executed. In FIG. 4A, the saturated vapor line of the organic medium is shown by a fine broken line, and the saturated liquid line of the organic medium is shown by a fine dashed line. That is, the organic medium is in a superheated steam state on the right side of the saturated steam line, in a supercooled state on the left side of the saturated liquid line, and in a boiling state between the saturated steam line and the saturated liquid line. As shown in FIG. 4A, when the battery heating mode is executed, the organic medium is compressed by the compression expander 51 and supplied to the evaporator 56 and the battery container 55 in the state of superheated steam. The organic medium compressed by the compression expander 51 is cooled by heat exchange between the cooling water and the battery 81 in the process of flowing through the evaporator 56 and the battery container 55, and is supplied to the electronic expansion valve 54 in the state of a supercooled liquid. .. The organic medium supplied to the electronic expansion valve 54 is depressurized by the electronic expansion valve 54 and supplied to the condenser 52 in the state of a supercooled liquid or a mixed phase state. The organic medium supplied from the electronic expansion valve 54 is heated by heat exchange with the outside air in the process of flowing through the condenser 52, and is supplied to the compression expander 51 in the state of superheated steam. Therefore, when the battery heating mode is executed, a part of the thermal energy of the outside air is supplied to the battery 81, which raises the temperature of the battery 81.

＜バッテリ冷却モード＞
図３Ｂは、バッテリ冷却モードの実行時にランキンサイクル回路５において実現される有機媒体の流れを示す図である。制御装置７は、バッテリ冷却モードでは、図３Ｂにおいて太矢印で示すように、有機媒体が第１の流れ方向Ｆ１に沿って、第１ポンプ５３、バッテリ容器５５、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で有機媒体が循環するようにランキンサイクル回路５を操作する。より具体的には、制御装置７は、バッテリ加温モードでは、第２ポンプ６１をオフにし、電子膨張弁５４を閉じるとともに、第１ポンプ５３をオンにし、圧縮膨張機５１を正転させる。バッテリ冷却モードでは、制御装置７によって上述のようにランキンサイクル回路５を操作することによって、図４Ａに示すような熱サイクルが実現される。 <Battery cooling mode>
FIG. 3B is a diagram showing the flow of the organic medium realized in the Rankine cycle circuit 5 when the battery cooling mode is executed. In the battery cooling mode, the control device 7 has a first pump 53, a battery container 55, an evaporator 56, and a compression expander 51 along the first flow direction F1 in which the organic medium is shown by a thick arrow in FIG. 3B. , And the condenser 52, and the Rankine cycle circuit 5 is operated so that the organic medium circulates in this order. More specifically, in the battery heating mode, the control device 7 turns off the second pump 61, closes the electronic expansion valve 54, turns on the first pump 53, and rotates the compression expander 51 in the forward direction. In the battery cooling mode, the control device 7 operates the Rankine cycle circuit 5 as described above to realize the thermal cycle as shown in FIG. 4A.

図４Ｂは、バッテリ冷却モードの実行時にランキンサイクル回路５において実現される熱サイクルを示すモリエル線図である。図４Ｂに示すように、バッテリ冷却モードの実行時には、有機媒体は、第１ポンプ５３によって圧縮され、過冷却液の状態でバッテリ容器５５及び蒸発器５６に供給される。第１ポンプ５３によって圧縮された有機媒体は、バッテリ容器５５及び蒸発器５６を流れる過程でバッテリ８１及び冷却水との熱交換によって加温され、過熱蒸気の状態で圧縮膨張機５１に供給される。蒸発器５６から過熱蒸気の状態で流出した有機媒体は、圧縮膨張機５１において減圧され、過熱蒸気の状態で凝縮器５２に供給される。圧縮膨張機５１から供給された有機媒体は、凝縮器５２を流れる過程で外気との熱交換によって冷却され、過冷却液の状態で第１ポンプ５３に供給される。このため、バッテリ冷却モードの実行時には、バッテリ８１の熱エネルギの一部が外気に放出されるため、これによりバッテリ８１の温度が低下する。ここで制御装置７は、バッテリ冷却モードでは、バッテリ容器５５内において有機媒体が沸騰した状態で維持されるように、換言すればバッテリ８１がバッテリ容器５５内において有機媒体の潜熱によって冷却されるように、第１ポンプ５３及びモータジェネレータ５７を操作する。 FIG. 4B is a Moriel diagram showing the thermal cycle realized in the Rankine cycle circuit 5 when the battery cooling mode is executed. As shown in FIG. 4B, when the battery cooling mode is executed, the organic medium is compressed by the first pump 53 and supplied to the battery container 55 and the evaporator 56 in the state of a supercooled liquid. The organic medium compressed by the first pump 53 is heated by heat exchange between the battery 81 and the cooling water in the process of flowing through the battery container 55 and the evaporator 56, and is supplied to the compression expander 51 in the state of superheated steam. .. The organic medium flowing out of the evaporator 56 in the state of superheated steam is depressurized in the compression expander 51 and supplied to the condenser 52 in the state of superheated steam. The organic medium supplied from the compression expander 51 is cooled by heat exchange with the outside air in the process of flowing through the condenser 52, and is supplied to the first pump 53 in the state of a supercooled liquid. Therefore, when the battery cooling mode is executed, a part of the thermal energy of the battery 81 is released to the outside air, which lowers the temperature of the battery 81. Here, in the battery cooling mode, the control device 7 is such that the organic medium is maintained in a boiling state in the battery container 55, in other words, the battery 81 is cooled by the latent heat of the organic medium in the battery container 55. The first pump 53 and the motor generator 57 are operated.

ここでバッテリ容器５５内における有機媒体の沸点は、バッテリ容器５５内における有機媒体の量及び圧力によって変化する。そこで制御装置７は、バッテリ冷却モードでは、バッテリ容器５５内における有機媒体の沸点がバッテリ８１の最適温度の近傍に定められた目標温度で維持されるように、第１ポンプ５３及びモータジェネレータ５７を用いてバッテリ容器５５内における有機媒体の量及び圧力を制御する。より具体的には、制御装置７は、バッテリ容器５５内における有機媒体の沸点が上記目標温度で維持されるように、バッテリ容器５５内における有機媒体の目標量及び目標圧を算出するとともに、バッテリ容器５５内における有機媒体の量が上記目標量になるように第１ポンプ５３の回転数を調整し、さらにバッテリ容器５５内における有機媒体の圧力が上記目標圧になるようにモータジェネレータ５７をジェネレータ、無負荷状態、又はモータとして作動させる。 Here, the boiling point of the organic medium in the battery container 55 changes depending on the amount and pressure of the organic medium in the battery container 55. Therefore, in the battery cooling mode, the control device 7 sets the first pump 53 and the motor generator 57 so that the boiling point of the organic medium in the battery container 55 is maintained at a target temperature determined in the vicinity of the optimum temperature of the battery 81. It is used to control the amount and pressure of the organic medium in the battery vessel 55. More specifically, the control device 7 calculates the target amount and the target pressure of the organic medium in the battery container 55 so that the boiling point of the organic medium in the battery container 55 is maintained at the target temperature, and the battery. The rotation speed of the first pump 53 is adjusted so that the amount of the organic medium in the container 55 becomes the above target amount, and the motor generator 57 is generated so that the pressure of the organic medium in the battery container 55 becomes the above target pressure. , No load, or operate as a motor.

＜第１エンジン冷却モード＞
図３Ｃは、第１及び第２エンジン冷却モードの実行時にランキンサイクル回路５において実現される有機媒体の流れを示す図である。制御装置７は、第１エンジン冷却モードでは、図３Ｃにおいて太矢印で示すように、有機媒体が第１の流れ方向Ｆ１に沿って、第２ポンプ６１、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で有機媒体が循環するようにランキンサイクル回路５を操作する。より具体的には、制御装置７は、第１エンジン冷却モードでは、第１ポンプ５３をオフにし、電子膨張弁５４を閉じるとともに、第２ポンプ６１をオンにし、圧縮膨張機５１を正転させる。第１エンジン冷却モードでは、制御装置７によって上述のようにランキンサイクル回路５を操作することによって、図４Ｃに示すような熱サイクルが実現される。 <1st engine cooling mode>
FIG. 3C is a diagram showing the flow of the organic medium realized in the Rankine cycle circuit 5 when the first and second engine cooling modes are executed. In the first engine cooling mode, the control device 7 has a second pump 61, an evaporator 56, a compression expander 51, and an organic medium along the first flow direction F1, as shown by a thick arrow in FIG. 3C. The Rankine cycle circuit 5 is operated so that the organic medium circulates in the order of the condenser 52. More specifically, in the first engine cooling mode, the control device 7 turns off the first pump 53, closes the electronic expansion valve 54, turns on the second pump 61, and rotates the compression expander 51 in the normal direction. .. In the first engine cooling mode, the thermal cycle as shown in FIG. 4C is realized by operating the Rankine cycle circuit 5 as described above by the control device 7.

図４Ｃは、第１及び第２エンジン冷却モードの実行時にランキンサイクル回路５において実現される熱サイクルを示すモリエル線図である。図４Ｃに示すように、第１エンジン冷却モードの実行時には、有機媒体は、第２ポンプ６１によって圧縮され、過冷却液の状態で蒸発器５６に供給される。第２ポンプ６１によって圧縮された有機媒体は、蒸発器５６を流れる過程で冷却水との熱交換によって加温され、過熱蒸気の状態で圧縮膨張機５１に供給される。蒸発器５６から過熱蒸気の状態で流出した有機媒体は、圧縮膨張機５１において減圧され、過熱蒸気の状態で凝縮器５２に供給される。圧縮膨張機５１から供給された有機媒体は、凝縮器５２を流れる過程で外気との熱交換によって冷却され、過冷却液の状態で第２ポンプ６１に供給される。ここで制御装置７は、第１エンジン冷却モードでは、圧縮膨張機５１において有機媒体を減圧させる過程で駆動軸５１ａにおいて生じる機械エネルギを利用することによってモータジェネレータ５７によって発電させ、これによって得られる電力でバッテリ８１を充電する。このため第１エンジン冷却モードの実行時には、冷却水の熱エネルギの一部が外気に放出されるとともにモータジェネレータ５７によって電気エネルギとして回収されるため、これにより冷却水及びエンジン２の温度が低下する。ここで制御装置７は、第１エンジン冷却モードでは、蒸発器５６内において有機媒体が沸騰した状態で維持されるように、換言すれば冷却水が蒸発器５６において有機媒体の潜熱によって冷却されるように、第２ポンプ６１及びモータジェネレータ５７を操作する。 FIG. 4C is a Moriel diagram showing the thermal cycle realized in the Rankine cycle circuit 5 when the first and second engine cooling modes are executed. As shown in FIG. 4C, when the first engine cooling mode is executed, the organic medium is compressed by the second pump 61 and supplied to the evaporator 56 in the state of a supercooled liquid. The organic medium compressed by the second pump 61 is heated by heat exchange with cooling water in the process of flowing through the evaporator 56, and is supplied to the compression expander 51 in the state of superheated steam. The organic medium flowing out of the evaporator 56 in the state of superheated steam is depressurized in the compression expander 51 and supplied to the condenser 52 in the state of superheated steam. The organic medium supplied from the compression expander 51 is cooled by heat exchange with the outside air in the process of flowing through the condenser 52, and is supplied to the second pump 61 in the state of a supercooled liquid. Here, in the first engine cooling mode, the control device 7 is generated by the motor generator 57 by utilizing the mechanical energy generated in the drive shaft 51a in the process of depressurizing the organic medium in the compression expander 51, and the electric power obtained by this is generated. Charges the battery 81 with. Therefore, when the first engine cooling mode is executed, a part of the thermal energy of the cooling water is released to the outside air and recovered as electric energy by the motor generator 57, which lowers the temperature of the cooling water and the engine 2. .. Here, in the first engine cooling mode, the control device 7 cools the cooling water in the evaporator 56 by the latent heat of the organic medium so that the organic medium is maintained in a boiling state in the evaporator 56. In this way, the second pump 61 and the motor generator 57 are operated.

ここで蒸発器５６における有機媒体の沸点は、蒸発器５６内における有機媒体の量及び圧力によって変化する。そこで制御装置７は、第１エンジン冷却モードでは、蒸発器５６における有機媒体の沸点が冷却水の目標温度で維持されるように、第２ポンプ６１及びモータジェネレータ５７を用いて蒸発器５６における有機媒体の量及び圧力を制御する。より具体的には、制御装置７は、蒸発器５６における有機媒体の沸点が上記目標温度で維持されるように、蒸発器５６における有機媒体の目標量及び目標圧を算出するとともに、蒸発器５６における有機媒体の量が上記目標量になるように第２ポンプ６１の回転数を調整し、さらに蒸発器５６における有機媒体の圧力が上記目標圧になるようにモータジェネレータ５７における発電量を調整する。 Here, the boiling point of the organic medium in the evaporator 56 changes depending on the amount and pressure of the organic medium in the evaporator 56. Therefore, in the first engine cooling mode, the control device 7 uses the second pump 61 and the motor generator 57 to maintain the boiling point of the organic medium in the evaporator 56 at the target temperature of the cooling water, so that the organic medium in the evaporator 56 is organic. Control the amount and pressure of the medium. More specifically, the control device 7 calculates the target amount and the target pressure of the organic medium in the evaporator 56 so that the boiling point of the organic medium in the evaporator 56 is maintained at the target temperature, and the evaporator 56 The rotation speed of the second pump 61 is adjusted so that the amount of the organic medium in the above target amount is obtained, and the amount of power generated by the motor generator 57 is adjusted so that the pressure of the organic medium in the evaporator 56 becomes the above target pressure. ..

以上のように第１エンジン冷却モードでは、制御装置７は、モータジェネレータ５７をジェネレータとして作動させることから、蒸発器５６内における圧力は、上述のバッテリ加温モード及びバッテリ冷却モードよりも高くなる（図２参照）。 As described above, in the first engine cooling mode, the control device 7 operates the motor generator 57 as a generator, so that the pressure in the evaporator 56 is higher than that in the battery heating mode and the battery cooling mode described above. (See FIG. 2).

＜第１ハイブリッド冷却モード＞
図３Ｄは、第１及び第２ハイブリッド冷却モードの実行時にランキンサイクル回路５において実現される有機媒体の流れを示す図である。制御装置７は、第１ハイブリッド冷却モードでは、図３Ｄにおいて太矢印で示すように、有機媒体が第１の流れ方向Ｆ１に沿って、第１ポンプ５３、バッテリ容器５５、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で構成される第１循環流路と、第２ポンプ６１、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で構成される第２循環流路と、の２つの循環流路に沿って有機媒体が循環するように、ランキンサイクル回路５を操作する。より具体的には、制御装置７は、第１ハイブリッド冷却モードでは、電子膨張弁５４を閉じるとともに、第１ポンプ５３及び第２ポンプ６１をオンにし、圧縮膨張機５１を正転させる。第１ハイブリッド冷却モードでは、制御装置７によって上述のようにランキンサイクル回路５を操作することによって、図４Ｄに示すような熱サイクルが実現される。 <1st hybrid cooling mode>
FIG. 3D is a diagram showing the flow of the organic medium realized in the Rankine cycle circuit 5 when the first and second hybrid cooling modes are executed. In the first hybrid cooling mode, the control device 7 has a first pump 53, a battery container 55, an evaporator 56, and a compression expansion along the first flow direction F1 as shown by a thick arrow in FIG. 3D. A first circulation flow path composed of the machine 51 and a condenser 52 in this order, and a second circulation flow path composed of a second pump 61, an evaporator 56, a compression expander 51, and a condenser 52 in this order. The Rankine cycle circuit 5 is operated so that the organic medium circulates along the two circulation channels of. More specifically, in the first hybrid cooling mode, the control device 7 closes the electronic expansion valve 54, turns on the first pump 53 and the second pump 61, and rotates the compression expander 51 in the normal direction. In the first hybrid cooling mode, the thermal cycle as shown in FIG. 4D is realized by operating the Rankine cycle circuit 5 as described above by the control device 7.

図４Ｄは、第１及び第２ハイブリッド冷却モードの実行時にランキンサイクル回路５において実現される熱サイクルを示すモリエル線図である。図４Ｄに示すように、第１ハイブリッド冷却モードの実行時には、有機媒体は、第１ポンプ５３によって圧縮され、過冷却液の状態でバッテリ容器５５に供給される。第１ポンプ５３によって圧縮された有機媒体は、バッテリ容器５５を流れる過程でバッテリ８１との熱交換によって加温され、過熱蒸気又は沸騰した状態で蒸発器５６に供給される。バッテリ容器５５から過熱蒸気又は沸騰した状態で流出した有機媒体は、蒸発器５６を流れる過程で冷却水との熱交換によってさらに加温され、過熱蒸気の状態で圧縮膨張機５１に供給される。蒸発器５６から過熱蒸気の状態で流出した有機媒体は、圧縮膨張機５１において減圧され、過熱蒸気の状態で凝縮器５２に供給される。圧縮膨張機５１から供給された有機媒体は、凝縮器５２を流れる過程で外気との熱交換によって冷却され、過冷却液の状態で第１ポンプ５３に供給される。また上述のように第１ハイブリッド冷却モードでは、第１ポンプ５３に加えて第２ポンプ６１をオンにする。このため、凝縮器５２から過冷却液の状態で流出する有機媒体の一部は、第２ポンプ６１によって圧縮され、第１ポンプ５３及びバッテリ容器５５を迂回し、過冷却液の状態で蒸発器５６に供給される。 FIG. 4D is a Moriel diagram showing the thermal cycle realized in the Rankine cycle circuit 5 during execution of the first and second hybrid cooling modes. As shown in FIG. 4D, when the first hybrid cooling mode is executed, the organic medium is compressed by the first pump 53 and supplied to the battery container 55 in the state of a supercooled liquid. The organic medium compressed by the first pump 53 is heated by heat exchange with the battery 81 in the process of flowing through the battery container 55, and is supplied to the evaporator 56 in a superheated steam or a boiling state. The superheated steam or the organic medium flowing out from the battery container 55 in a boiling state is further heated by heat exchange with cooling water in the process of flowing through the evaporator 56, and is supplied to the compression expander 51 in the state of superheated steam. The organic medium flowing out of the evaporator 56 in the state of superheated steam is depressurized in the compression expander 51 and supplied to the condenser 52 in the state of superheated steam. The organic medium supplied from the compression expander 51 is cooled by heat exchange with the outside air in the process of flowing through the condenser 52, and is supplied to the first pump 53 in the state of a supercooled liquid. Further, as described above, in the first hybrid cooling mode, the second pump 61 is turned on in addition to the first pump 53. Therefore, a part of the organic medium flowing out from the condenser 52 in the state of supercooled liquid is compressed by the second pump 61, bypasses the first pump 53 and the battery container 55, and evaporates in the state of supercooled liquid. It is supplied to 56.

ここで制御装置７は、第１ハイブリッド冷却モードでは、圧縮膨張機５１において有機媒体を減圧させる過程で駆動軸５１ａにおいて生じる機械エネルギを利用することによってモータジェネレータ５７によって発電させ、これによって得られる電力でバッテリ８１を充電する。このため第１ハイブリッド冷却モードの実行時には、バッテリ８１の熱エネルギの一部及び冷却水の熱エネルギの一部が、外気に放出されるとともにモータジェネレータ５７によって電気エネルギとして回収されるため、これによりバッテリ８１及び冷却水及びエンジン２の温度が低下する。 Here, in the first hybrid cooling mode, the control device 7 is generated by the motor generator 57 by utilizing the mechanical energy generated in the drive shaft 51a in the process of depressurizing the organic medium in the compression expander 51, and the electric power obtained by this is generated. Charges the battery 81 with. Therefore, when the first hybrid cooling mode is executed, a part of the thermal energy of the battery 81 and a part of the thermal energy of the cooling water are released to the outside air and recovered as electric energy by the motor generator 57. The temperature of the battery 81, the cooling water, and the engine 2 drops.

ここで制御装置７は、第１ハイブリッド冷却モードでは、バッテリ容器５５からは沸点よりもやや低い温度で有機媒体が流出し、かつ蒸発器５６内において有機媒体が沸騰した状態で維持されるように、換言すれば、バッテリ８１がバッテリ容器５５内において有機媒体の顕熱によって冷却され、かつ冷却水が蒸発器５６内において有機媒体の潜熱によって冷却されるように、第１ポンプ５３、第２ポンプ６１、及びモータジェネレータ５７を操作する。 Here, in the first hybrid cooling mode, the control device 7 causes the organic medium to flow out from the battery container 55 at a temperature slightly lower than the boiling point, and the organic medium is maintained in a boiling state in the evaporator 56. In other words, the first pump 53 and the second pump so that the battery 81 is cooled by the sensible heat of the organic medium in the battery container 55 and the cooling water is cooled by the latent heat of the organic medium in the evaporator 56. The 61 and the motor generator 57 are operated.

上述のように蒸発器５６における有機媒体の沸点は、蒸発器５６内における有機媒体の量及び圧力によって変化する。そこで制御装置７は、第１ハイブリッド冷却モードでは、バッテリ容器５５から流出する有機媒体の温度が沸点よりもやや低い温度で流出し、かつ蒸発器５６における有機媒体の沸点が冷却水の目標温度で維持されるように、第１ポンプ５３、第２ポンプ６１、及びモータジェネレータ５７を用いて蒸発器５６における有機媒体の量及び圧力を制御する。より具体的には、制御装置７は、バッテリ容器５５からは有機媒体が沸点よりもやや低い温度で流出しかつ蒸発器５６における有機媒体の沸点が上記目標温度で維持されるように、バッテリ容器５５における有機媒体の目標量並びに蒸発器５６における有機媒体の目標量及び目標圧を算出するとともに、バッテリ容器５５における有機媒体の量が上記目標量になるように第１ポンプ５３の回転数を調整し、蒸発器５６における有機媒体の量が上記目標量になるように第２ポンプ６１の回転数を調整し、さらに蒸発器５６における有機媒体の圧力が上記目標圧になるようにモータジェネレータ５７における発電量を調整する。 As described above, the boiling point of the organic medium in the evaporator 56 changes depending on the amount and pressure of the organic medium in the evaporator 56. Therefore, in the first hybrid cooling mode, the control device 7 causes the temperature of the organic medium flowing out of the battery container 55 to flow out at a temperature slightly lower than the boiling point, and the boiling point of the organic medium in the evaporator 56 is the target temperature of the cooling water. A first pump 53, a second pump 61, and a motor generator 57 are used to control the amount and pressure of the organic medium in the evaporator 56 so that it is maintained. More specifically, the control device 7 uses the battery container so that the organic medium flows out from the battery container 55 at a temperature slightly lower than the boiling point and the boiling point of the organic medium in the evaporator 56 is maintained at the target temperature. The target amount of the organic medium in the 55 and the target amount and the target pressure of the organic medium in the evaporator 56 are calculated, and the rotation speed of the first pump 53 is adjusted so that the amount of the organic medium in the battery container 55 becomes the above target amount. Then, the rotation speed of the second pump 61 is adjusted so that the amount of the organic medium in the evaporator 56 becomes the above target amount, and the motor generator 57 further adjusts the pressure of the organic medium in the evaporator 56 to the above target pressure. Adjust the amount of power generation.

以上のように第１ハイブリッド冷却モードでは、制御装置７は、モータジェネレータ５７をジェネレータとして作動させることから、蒸発器５６内における圧力は、上述のバッテリ加温モード及びバッテリ冷却モードよりも高くなる（図２参照）。 As described above, in the first hybrid cooling mode, the control device 7 operates the motor generator 57 as a generator, so that the pressure in the evaporator 56 is higher than that in the battery heating mode and the battery cooling mode described above. (See FIG. 2).

＜第２エンジン冷却モード＞
制御装置７は、第２エンジン冷却モードでは、上述の第１エンジン冷却モードと同様に、図３Ｃにおいて太矢印で示すように、有機媒体が第１の流れ方向Ｆ１に沿って、第２ポンプ６１、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で有機媒体が循環するようにランキンサイクル回路５を操作する。これにより、第２バッテリ冷却モードでは、図４Ｃに示すように、第１バッテリ冷却モードと定性的に同様の熱サイクルが実現される。 <Second engine cooling mode>
In the second engine cooling mode, the control device 7 has the organic medium flowing along the first flow direction F1 along the first flow direction F1 as shown by the thick arrow in FIG. 3C, similarly to the first engine cooling mode described above. The Rankine cycle circuit 5 is operated so that the organic medium circulates in the order of the evaporator 56, the compression expander 51, and the condenser 52. As a result, in the second battery cooling mode, as shown in FIG. 4C, a heat cycle qualitatively similar to that in the first battery cooling mode is realized.

図２を参照して説明したように、制御装置７は、バッテリ８１がバッテリ加温要求状態であり、冷却水温度が廃熱回収可能温度以上でありかつエンジン保護温度より低い場合には第１エンジン冷却モードを実行し、バッテリ８１がバッテリ加温要求状態であり、冷却水温度がエンジン保護温度以上でありエンジン２及びその冷却水を速やかに冷却する必要がある場合には第２エンジン冷却モードを実行する。そこで制御装置７は、第２エンジン冷却モードでは、冷却水を速やかに冷却できるように、モータジェネレータ５７を無負荷状態とするか、又はバッテリ８１の電力をモータジェネレータ５７に供給することによってモータジェネレータ５７で圧縮膨張機５１を駆動する。これにより、第２エンジン冷却モードでは、蒸発器５６内における圧力は、上述の第１エンジン冷却モード及び第１ハイブリッド冷却モードよりも低くなる（図２参照）。 As described with reference to FIG. 2, the control device 7 is the first when the battery 81 is in the battery heating request state, the cooling water temperature is equal to or higher than the waste heat recovery temperature, and the temperature is lower than the engine protection temperature. When the engine cooling mode is executed, the battery 81 is in the battery heating request state, the cooling water temperature is equal to or higher than the engine protection temperature, and the engine 2 and its cooling water need to be cooled promptly, the second engine cooling mode is executed. To execute. Therefore, in the second engine cooling mode, the control device 7 puts the motor generator 57 in a no-load state or supplies the electric power of the battery 81 to the motor generator 57 so that the cooling water can be cooled quickly. The compression expander 51 is driven by 57. As a result, in the second engine cooling mode, the pressure in the evaporator 56 becomes lower than that in the first engine cooling mode and the first hybrid cooling mode described above (see FIG. 2).

＜第２ハイブリッド冷却モード＞
制御装置７は、第２ハイブリッド冷却モードでは、上述の第１ハイブリッド冷却モードと同様に、図３Ｄにおいて太矢印で示すように、有機媒体が第１の流れ方向Ｆ１に沿って、第１ポンプ５３、バッテリ容器５５、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で構成される第１循環流路と、第２ポンプ６１、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で構成される第２循環流路と、の２つの循環流路に沿って有機媒体が循環するように、ランキンサイクル回路５を操作する。これにより、第２ハイブリッド冷却モードでは、図４Ｄに示すように、第１ハイブリッド冷却モードと定性的に同様の熱サイクルが実現される。 <Second hybrid cooling mode>
In the second hybrid cooling mode, the control device 7 has the organic medium along the first flow direction F1 along the first flow direction F1 as shown by the thick arrow in FIG. 3D, similarly to the first hybrid cooling mode described above. , The first circulation flow path composed of the battery container 55, the evaporator 56, the compression expander 51, and the condenser 52 in this order, and the second pump 61, the evaporator 56, the compression expander 51, and the condenser 52. The Rankine cycle circuit 5 is operated so that the organic medium circulates along the second circulation flow path formed in order and the two circulation flow paths. As a result, in the second hybrid cooling mode, as shown in FIG. 4D, a heat cycle qualitatively similar to that in the first hybrid cooling mode is realized.

図２を参照して説明したように、制御装置７は、バッテリ８１がバッテリ冷却要求状態であり、冷却水温度が廃熱回収可能温度以上でありかつエンジン保護温度より低い場合には第１ハイブリッド冷却モードを実行し、バッテリ８１がバッテリ冷却要求状態であり、冷却水温度がエンジン保護温度以上でありエンジン２及びその冷却水を速やかに冷却する必要がある場合には第２ハイブリッド冷却モードを実行する。そこで制御装置７は、第２ハイブリッド冷却モードでは、冷却水を速やかに冷却できるように、モータジェネレータ５７を無負荷状態とするか、又はバッテリ８１の電力をモータジェネレータ５７に供給することによってモータジェネレータ５７で圧縮膨張機５１を駆動する。これにより、第２ハイブリッド冷却モードでは、蒸発器５６内における圧力は、上述の第１エンジン冷却モード及び第１ハイブリッド冷却モードよりも低くなる（図２参照）。 As described with reference to FIG. 2, the control device 7 is the first hybrid when the battery 81 is in the battery cooling required state and the cooling water temperature is equal to or higher than the waste heat recovery temperature and lower than the engine protection temperature. The cooling mode is executed, and when the battery 81 is in the battery cooling required state, the cooling water temperature is equal to or higher than the engine protection temperature, and the engine 2 and its cooling water need to be cooled promptly, the second hybrid cooling mode is executed. To do. Therefore, in the second hybrid cooling mode, the control device 7 puts the motor generator 57 in a no-load state or supplies the electric power of the battery 81 to the motor generator 57 so that the cooling water can be cooled quickly. The compression expander 51 is driven by 57. As a result, in the second hybrid cooling mode, the pressure in the evaporator 56 becomes lower than that in the first engine cooling mode and the first hybrid cooling mode described above (see FIG. 2).

本実施形態の熱サイクルシステム１によれば、以下の効果を奏する。
（１）制御装置７は、エンジン２の冷却水温度が廃熱回収可能温度より高く、エンジン２の廃熱によってモータジェネレータ５７で発電させることができる場合には、蒸発器５６、圧縮膨張機５１、及び凝縮器５２の順で有機媒体が循環するようにランキンサイクル回路５を操作する。このように有機媒体を循環させると、有機媒体は、蒸発器５６においてエンジン２及びその排気によって加温された冷却水によって加温され、圧縮膨張機５１において減圧され、凝縮器５２において外気との熱交換によって冷却される。これにより冷却水温度が廃熱回収可能温度より高い場合には、エンジン２の廃熱の一部を、圧縮膨張機５１において有機媒体を減圧する過程で、モータジェネレータ５７によって電気エネルギとして回収できる。また熱サイクルシステム１において、ランキンサイクル回路５は、主循環流路５０において第１の流れ方向Ｆ１に沿って流れる有機媒体を減圧する電子膨張弁５４と、主循環流路５０内のバッテリ容器５５において有機媒体と熱交換が可能なバッテリ８１と、を備える。また制御装置７は、冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が加温要求状態である場合には、圧縮膨張機５１、バッテリ容器５５、電子膨張弁５４、及び凝縮器５２の順で有機媒体が循環するようにランキンサイクル回路５を操作する。このように有機媒体を循環させると、有機媒体は、圧縮膨張機５１において圧縮され、バッテリ容器５５においてバッテリ８１との熱交換によって冷却され、電子膨張弁５４によって減圧され、凝縮器５２において外気との熱交換によって加温される。これにより冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が加温要求状態である場合には、外気の熱エネルギの一部をバッテリ８１に与えることにより、バッテリ８１を加温できる。以上より熱サイクルシステム１によれば、エンジン２の廃熱回収とバッテリ８１の加温との両方を行うことができる。 According to the thermal cycle system 1 of the present embodiment, the following effects are obtained.
(1) When the temperature of the cooling water of the engine 2 is higher than the temperature at which the waste heat can be recovered and the waste heat of the engine 2 can generate electricity with the motor generator 57, the control device 7 has an evaporator 56 and a compression expander 51. The Rankine cycle circuit 5 is operated so that the organic medium circulates in the order of the condenser 52 and the condenser 52. When the organic medium is circulated in this way, the organic medium is heated by the cooling water heated by the engine 2 and its exhaust in the evaporator 56, depressurized by the compression expander 51, and with the outside air in the condenser 52. It is cooled by heat exchange. As a result, when the cooling water temperature is higher than the waste heat recoverable temperature, a part of the waste heat of the engine 2 can be recovered as electric energy by the motor generator 57 in the process of depressurizing the organic medium in the compression expander 51. Further, in the heat cycle system 1, the Rankine cycle circuit 5 includes an electronic expansion valve 54 for reducing the pressure of the organic medium flowing along the first flow direction F1 in the main circulation flow path 50, and a battery container 55 in the main circulation flow path 50. A battery 81 capable of heat exchange with an organic medium is provided. Further, in the control device 7, when the cooling water temperature is equal to or lower than the waste heat recovery temperature and the battery 81 is in a heating required state, the compression expander 51, the battery container 55, the electronic expansion valve 54, and the condenser 52 The Rankine cycle circuit 5 is operated so that the organic medium circulates in the order of. When the organic medium is circulated in this way, the organic medium is compressed in the compression expander 51, cooled by heat exchange with the battery 81 in the battery container 55, decompressed by the electronic expansion valve 54, and with the outside air in the condenser 52. It is heated by heat exchange. As a result, when the cooling water temperature is equal to or lower than the waste heat recoverable temperature and the battery 81 is in a heating required state, the battery 81 can be heated by giving a part of the heat energy of the outside air to the battery 81. From the above, according to the thermal cycle system 1, both the waste heat recovery of the engine 2 and the heating of the battery 81 can be performed.

（２）主循環流路５０には、上述のように第１の流れ方向Ｆ１に沿って流れる有機媒体を減圧する電子膨張弁５４と、これとは逆に第２の流れ方向Ｆ２に沿って流れる有機媒体を圧縮する第１ポンプ５３とを並列に設ける。また制御装置７は、冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が冷却要求状態である場合には、第１ポンプ５３、バッテリ容器５５、圧縮膨張機５１、及び凝縮器５２の順で有機媒体が循環するようにランキンサイクル回路５を操作する。このように有機媒体を循環させると、有機媒体は、第１ポンプ５３によって圧縮され、バッテリ容器５５においてバッテリ８１との熱交換によって加温され、圧縮膨張機５１において減圧され、凝縮器５２において外気との熱交換によって冷却される。これにより冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が冷却要求状態である場合には、バッテリ８１の熱エネルギの一部を外気に放出することにより、バッテリ８１を冷却できる。以上より熱サイクルシステム１によれば、エンジン２の廃熱回収と、バッテリ８１の加温及び冷却とを行うことができる。 (2) The main circulation flow path 50 has an electron expansion valve 54 for reducing the pressure of the organic medium flowing along the first flow direction F1 as described above, and conversely, along the second flow direction F2. A first pump 53 for compressing the flowing organic medium is provided in parallel. Further, when the cooling water temperature is equal to or lower than the waste heat recovery temperature and the battery 81 is in the cooling required state, the control device 7 of the first pump 53, the battery container 55, the compression expander 51, and the condenser 52. The Rankine cycle circuit 5 is operated so that the organic medium circulates in order. When the organic medium is circulated in this way, the organic medium is compressed by the first pump 53, heated by heat exchange with the battery 81 in the battery container 55, depressurized in the compression expander 51, and outside air in the condenser 52. It is cooled by heat exchange with. As a result, when the cooling water temperature is equal to or lower than the waste heat recoverable temperature and the battery 81 is in the cooling required state, the battery 81 can be cooled by releasing a part of the thermal energy of the battery 81 to the outside air. From the above, according to the thermal cycle system 1, it is possible to recover the waste heat of the engine 2 and heat and cool the battery 81.

（５）制御装置７は、冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が冷却要求状態である場合には、バッテリ８１との間で熱交換が可能なバッテリ容器５５において有機媒体が沸騰した状態で維持されるように第１ポンプ５３及びモータジェネレータ５７を操作する。熱サイクルシステム１によれば、冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が冷却要求状態である場合には、バッテリ容器５５においてバッテリ８１を有機媒体の潜熱によって冷却できるので、バッテリ８１を効果的に冷却できる。 (5) The control device 7 is an organic medium in the battery container 55 capable of exchanging heat with the battery 81 when the cooling water temperature is equal to or lower than the waste heat recoverable temperature and the battery 81 is in a cooling required state. The first pump 53 and the motor generator 57 are operated so that the temperature is maintained in a boiling state. According to the thermal cycle system 1, when the cooling water temperature is equal to or lower than the waste heat recovery temperature and the battery 81 is in the cooling required state, the battery 81 can be cooled by the latent heat of the organic medium in the battery container 55, so that the battery 81 can be effectively cooled.

（６）制御装置７は、冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が冷却要求状態である場合には、バッテリ容器５５における有機媒体の沸点がバッテリ８１の目標温度で維持されるように、第１ポンプ５３及びモータジェネレータ５７を用いてバッテリ容器５５における有機媒体の量及び圧力を制御する。熱サイクルシステム１によれば、冷却水温度が廃熱回収可能温度以下でありかつバッテリ８１が冷却要求状態である場合には、バッテリ容器５５においてバッテリ８１を有機媒体の潜熱によって冷却しながら、この有機媒体の温度をバッテリ８１の目標温度で維持できるので、バッテリ８１を速やかに目標温度まで低下させることができる。 (6) In the control device 7, when the cooling water temperature is equal to or lower than the waste heat recovery temperature and the battery 81 is in the cooling required state, the boiling point of the organic medium in the battery container 55 is maintained at the target temperature of the battery 81. As described above, the first pump 53 and the motor generator 57 are used to control the amount and pressure of the organic medium in the battery container 55. According to the thermal cycle system 1, when the cooling water temperature is equal to or lower than the waste heat recoverable temperature and the battery 81 is in a cooling required state, the battery 81 is cooled by the latent heat of the organic medium in the battery container 55. Since the temperature of the organic medium can be maintained at the target temperature of the battery 81, the battery 81 can be quickly lowered to the target temperature.

以上、本発明の一実施形態について説明したが、本発明はこれに限らない。本発明の趣旨の範囲内で、細部の構成を適宜変更してもよい。 Although one embodiment of the present invention has been described above, the present invention is not limited to this. Within the scope of the gist of the present invention, the detailed configuration may be changed as appropriate.

１…熱サイクルシステム
２…エンジン（内燃機関）
３…冷却回路
５…ランキンサイクル回路
５０…主循環流路
５１…圧縮膨張機
５２…凝縮器（第１熱交換器）
５３…第１ポンプ（ポンプ）
５４…電子膨張弁（膨張弁）
５５…バッテリ容器（熱交換部）
５６…蒸発器（第２熱交換器）
５７…モータジェネレータ
６０…バイパス流路
６１…第２ポンプ
７…制御装置
８１…バッテリ（蓄電装置） 1 ... Thermal cycle system 2 ... Engine (internal combustion engine)
3 ... Cooling circuit 5 ... Rankine cycle circuit 50 ... Main circulation flow path 51 ... Compression expander 52 ... Condenser (first heat exchanger)
53 ... 1st pump (pump)
54 ... Electronic expansion valve (expansion valve)
55 ... Battery container (heat exchange section)
56 ... Evaporator (second heat exchanger)
57 ... Motor generator 60 ... Bypass flow path 61 ... Second pump 7 ... Control device 81 ... Battery (power storage device)

Claims (6)

内燃機関及びその排気と熱交換を行う冷却水が循環する冷却回路と、
絶縁性の有機媒体が循環する循環流路、前記循環流路に設けられ有機媒体と外気との間で熱交換を行う第１熱交換器、前記循環流路に設けられ有機媒体と冷却水との間で熱交換を行う第２熱交換器、前記循環流路に設けられ前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮し、前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する圧縮膨張機、及び前記圧縮膨張機に接続されたモータジェネレータを備えるランキンサイクル回路と、
前記内燃機関又は当該内燃機関と相関のある部分の温度である内燃機関温度が所定の廃熱回収可能温度より高い場合には、前記第２熱交換器、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作する制御装置と、を備える熱サイクルシステムであって、
前記ランキンサイクル回路は、前記循環流路に設けられ前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する膨張弁と、前記循環流路内の熱交換部において有機媒体と熱交換が可能な蓄電装置と、を備え、
前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が加温要求状態である場合には、前記圧縮膨張機、前記熱交換部、前記膨張弁、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することを特徴とする熱サイクルシステム。 A cooling circuit that circulates cooling water that exchanges heat with the internal combustion engine and its exhaust gas,
A circulation flow path in which an insulating organic medium circulates, a first heat exchanger provided in the circulation flow path for heat exchange between the organic medium and the outside air, and an organic medium and cooling water provided in the circulation flow path. A second heat exchanger that exchanges heat between the two, the organic medium that is provided in the circulation flow path and flows from the first heat exchanger side to the second heat exchanger side is compressed, and the second heat exchanger side. A Rankin cycle circuit including a compression expander for reducing the pressure of the organic medium flowing from the first heat exchanger to the first heat exchanger side and a motor generator connected to the compression expander.
When the internal combustion engine temperature, which is the temperature of the internal combustion engine or a portion correlated with the internal combustion engine, is higher than the predetermined waste heat recoverable temperature, the second heat exchanger, the compression expander, and the first heat. A thermal cycle system comprising a control device that operates the Rankine cycle circuit so that the organic medium circulates in the order of the exchangers.
The Rankine cycle circuit includes an expansion valve provided in the circulation flow path for reducing the pressure of the organic medium flowing from the second heat exchanger side to the first heat exchanger side, and an organic heat exchange section in the circulation flow path. Equipped with a power storage device that can exchange heat with the medium,
When the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a heating request state, the control device includes the compression expander, the heat exchange unit, the expansion valve, and the control device. A heat cycle system characterized in that the Rankine cycle circuit is operated so that an organic medium circulates in the order of the first heat exchanger. 前記循環流路には、前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮するポンプが前記膨張弁と並列になるように設けられ、
前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が冷却要求状態である場合には、前記ポンプ、前記熱交換部、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することを特徴とする請求項１に記載の熱サイクルシステム。 A pump for compressing the organic medium flowing from the first heat exchanger side to the second heat exchanger side is provided in the circulation flow path in parallel with the expansion valve.
When the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a cooling request state, the control device includes the pump, the heat exchange unit, the compression expander, and the first. The heat cycle system according to claim 1, wherein the Rankine cycle circuit is operated so that the organic medium circulates in the order of the heat exchanger. 内燃機関及びその排気と熱交換を行う冷却水が循環する冷却回路と、
絶縁性の有機媒体が循環する循環流路、前記循環流路に設けられ有機媒体と外気との間で熱交換を行う第１熱交換器、前記循環流路に設けられ有機媒体と冷却水との間で熱交換を行う第２熱交換器、前記循環流路に設けられ前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮し、前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する圧縮膨張機、及び前記圧縮膨張機に接続されたモータジェネレータを備えるランキンサイクル回路と、
前記内燃機関又は当該内燃機関と相関のある部分の温度である内燃機関温度が所定の廃熱回収可能温度より高い場合には、前記第２熱交換器、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作する制御装置と、を備える熱サイクルシステムであって、
前記ランキンサイクル回路は、前記循環流路に設けられ前記第１熱交換器側から前記第２熱交換器側へ流れる有機媒体を圧縮するポンプと、前記循環流路内の熱交換部において有機媒体と熱交換が可能な蓄電装置と、を備え、
前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が冷却要求状態である場合には、前記ポンプ、前記熱交換部、前記圧縮膨張機、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することを特徴とする熱サイクルシステム。 A cooling circuit that circulates cooling water that exchanges heat with the internal combustion engine and its exhaust gas,
A circulation flow path in which an insulating organic medium circulates, a first heat exchanger provided in the circulation flow path for heat exchange between the organic medium and the outside air, and an organic medium and cooling water provided in the circulation flow path. A second heat exchanger that exchanges heat between the two, the organic medium that is provided in the circulation flow path and flows from the first heat exchanger side to the second heat exchanger side is compressed, and the second heat exchanger side. A Rankin cycle circuit including a compression expander for reducing the pressure of the organic medium flowing from the first heat exchanger to the first heat exchanger side and a motor generator connected to the compression expander.
When the internal combustion engine temperature, which is the temperature of the internal combustion engine or a portion correlated with the internal combustion engine, is higher than the predetermined waste heat recoverable temperature, the second heat exchanger, the compression expander, and the first heat. A thermal cycle system comprising a control device that operates the Rankine cycle circuit so that the organic medium circulates in the order of the exchangers.
The Rankine cycle circuit includes a pump provided in the circulation flow path for compressing an organic medium flowing from the first heat exchanger side to the second heat exchanger side, and an organic medium in a heat exchange section in the circulation flow path. Equipped with a power storage device that can exchange heat with
When the temperature of the internal combustion engine is equal to or lower than the waste heat recovery temperature and the power storage device is in a cooling required state, the control device includes the pump, the heat exchange unit, the compression expander, and the first. A heat cycle system characterized in that the Rankine cycle circuit is operated so that an organic medium circulates in the order of heat exchangers. 前記循環流路には、前記第２熱交換器側から前記第１熱交換器側へ流れる有機媒体を減圧する膨張弁が前記ポンプと並列になるように設けられ、
前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が加温要求状態である場合には、前記圧縮膨張機、前記熱交換部、前記膨張弁、及び前記第１熱交換器の順で有機媒体が循環するように前記ランキンサイクル回路を操作することを特徴とする請求項３に記載の熱サイクルシステム。 An expansion valve for reducing the pressure of the organic medium flowing from the second heat exchanger side to the first heat exchanger side is provided in the circulation flow path in parallel with the pump.
When the internal combustion engine temperature is equal to or lower than the waste heat recoverable temperature and the power storage device is in a heating request state, the control device includes the compression expander, the heat exchange unit, the expansion valve, and the control device. The heat cycle system according to claim 3, wherein the Rankine cycle circuit is operated so that the organic medium circulates in the order of the first heat exchanger. 前記循環流路には、第１の流れ方向に沿って順に、前記ポンプと、前記熱交換部と、前記第２熱交換器と、前記圧縮膨張機と、前記第１熱交換器と、が設けられ、
前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が前記冷却要求状態である場合には、前記熱交換部における有機媒体が沸騰した状態で維持されるように、前記ポンプ及び前記モータジェネレータを操作することを特徴とする請求項２から４の何れかに記載の熱サイクルシステム。 In the circulation flow path, the pump, the heat exchange unit, the second heat exchanger, the compression expander, and the first heat exchanger are arranged in order along the first flow direction. Provided,
When the internal combustion engine temperature is equal to or lower than the waste heat recovery temperature and the power storage device is in the cooling required state, the control device is maintained in a boiling state of the organic medium in the heat exchange unit. The thermal cycle system according to any one of claims 2 to 4, wherein the pump and the motor generator are operated. 前記制御装置は、前記内燃機関温度が前記廃熱回収可能温度以下でありかつ前記蓄電装置が前記冷却要求状態である場合には、前記熱交換部における有機媒体の沸点が前記蓄電装置の目標温度で維持されるように、前記ポンプ及び前記モータジェネレータを用いて前記熱交換部における有機媒体の量及び圧力を制御することを特徴とする請求項５に記載の熱サイクルシステム。 In the control device, when the internal combustion engine temperature is equal to or lower than the waste heat recovery temperature and the power storage device is in the cooling required state, the boiling point of the organic medium in the heat exchange unit is the target temperature of the power storage device. The heat cycle system according to claim 5, wherein the pump and the motor generator are used to control the amount and pressure of the organic medium in the heat exchange section so as to be maintained in the above.
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