CN112186291B - Thermal circulation system - Google Patents

Thermal circulation system Download PDF

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Publication number
CN112186291B
CN112186291B CN202010631742.XA CN202010631742A CN112186291B CN 112186291 B CN112186291 B CN 112186291B CN 202010631742 A CN202010631742 A CN 202010631742A CN 112186291 B CN112186291 B CN 112186291B
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China
Prior art keywords
organic medium
battery
flow path
pump
flow direction
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CN202010631742.XA
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Chinese (zh)
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CN112186291A (en
Inventor
岩间恵三
土佐真一
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Honda Motor Co Ltd
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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
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • 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)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (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

The invention provides a thermal cycle system capable of adjusting the temperature of a battery according to a Rankine cycle circuit capable of performing heat exchange with cooling water of an engine. In order to solve the above problems, a thermal cycle system 1 is provided with: a cooling circuit 3 in which cooling water of the engine 2 circulates; and a Rankine cycle circuit 5 in which an insulating organic medium is circulated. The main circulation flow path 50 of the rankine cycle 5 is provided with a compression expander 51 for decompressing the organic medium, a condenser 52 for exchanging heat between the organic medium and the outside air, and a first pump 53 for compressing the organic medium in this order along the first flow direction F1, and a battery container 55 through which the organic medium flows and an evaporator 56 for exchanging heat between the organic medium and the cooling water of the cooling circuit 3 are provided between the first pump 53 and the compression expander 51 in the main circulation flow path 50, and a battery 81 is provided inside the battery container 55 so as to be immersed in the organic medium.

Description

Thermal circulation system
Technical Field
The present invention relates to a thermal cycle system. More specifically, the present invention relates to a thermal cycle system including a rankine cycle (RANKINE CYCLE) circuit.
Background
In recent years, a waste heat recovery system has been developed that extracts mechanical energy, electric energy, and the like from waste heat of an internal combustion engine of a vehicle using a rankine cycle. In such a waste heat regeneration system, a rankine cycle that extracts energy from waste heat is implemented according to a rankine cycle circuit that includes: a pump that pumps a working medium; a heat exchanger that can exchange heat between the working medium and cooling water of the internal combustion engine; an expander that expands the working medium heated by the heat exchanger to thereby generate mechanical energy and electrical energy; and a condenser that condenses the working medium expanded by the expander (refer to, for example, patent document 1).
[ Prior Art literature ]
(Patent literature)
Patent document 1: japanese patent laid-open No. 2006-118754
Disclosure of Invention
[ Problem to be solved by the invention ]
However, in a so-called hybrid vehicle including an electric motor as a driving force generation source in addition to an internal combustion engine, a battery temperature control system is mounted 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 a rankine cycle circuit capable of heat exchange with cooling water of an internal combustion engine as described above, a heater for heating the battery, a cooling circuit for cooling the battery, and the like are required, and the number of parts, weight, cost, and the like of the entire vehicle may be increased.
The present invention aims to provide a thermal cycle system capable of adjusting the temperature of a battery according to a Rankine cycle.
[ Means of solving the problems ]
(1) A thermal cycle system (for example, a thermal cycle system 1 described below) of the present invention includes a rankine cycle circuit (for example, a rankine cycle circuit 5 described below) in which an insulating organic medium is circulated, and is characterized in that: the circulation flow path (for example, a main circulation flow path 50 described later) of the rankine cycle circuit is provided with, in order, a first flow direction (for example, a first flow direction F1 described later): an expander (for example, a compression expander 51 described later) that decompresses the organic medium flowing in the first flow direction; a first heat exchanger (for example, a condenser 52 described later) that performs heat exchange between the organic medium and outside air; and a first pump (for example, a first pump 53 described later) that compresses the organic medium flowing in the first flow direction; a container (for example, a battery container 55 described later) through which an organic medium flows is provided between the first pump and the expander in the circulation flow path, and a power storage device (for example, a battery 81 described later) is provided in the container so as to be immersed in the organic medium.
(2) In this case, it is preferable that a cooling circuit (for example, a cooling circuit 3 described later) is further provided, in which cooling water that exchanges heat with the internal combustion engine (for example, an engine 2 described later) and its exhaust gas are circulated, the circulation flow path is provided with the container and a second heat exchanger (for example, an evaporator 56 described later) that exchanges heat between the organic medium and the cooling water of the cooling circuit in this order in the first flow direction, the rankine cycle circuit is provided with a bypass flow path (for example, a bypass flow path 60 described later) that connects between the first heat exchanger and the first pump among the circulation flow paths and between the container and the second heat exchanger, and the bypass flow path is provided with a second pump (for example, a second pump 61 described later) that compresses the organic medium flowing in the first flow direction.
(3) A thermal cycle system (for example, a thermal cycle system 1 described below) of the present invention includes a rankine cycle circuit (for example, a rankine cycle circuit 5 described below) in which an insulating organic medium is circulated, and is characterized in that: the circulation flow path (for example, a main circulation flow path 50 described later) of the rankine cycle circuit is provided with, in order, a second flow direction (for example, a second flow direction F2 described later): an expansion valve (for example, an electronic expansion valve 54 described later) that depressurizes the organic medium flowing in the second flow direction; a first heat exchanger (for example, a condenser 52 described later) that performs heat exchange between the organic medium and outside air; and a compressor (for example, a compression expander 51 described later) that compresses the organic medium flowing in the second flow direction; a container (for example, a battery container 55 described later) through which an organic medium flows is provided between the compressor and the expansion valve in the circulation flow path, and a power storage device (for example, a battery 81 described later) is provided in the container so as to be immersed in the organic medium.
(4) In this case, the compressor is preferably a compression expander (for example, a compression expander 51 described later) that compresses the organic medium flowing in the second flow direction and decompresses the organic medium flowing in a first flow direction opposite to the second flow direction, and the expansion valve and a first pump (for example, a first pump 53 described later) that compresses the organic medium flowing in the first flow direction are disposed in parallel in the circulation flow path.
(5) In this case, it is preferable that a cooling circuit (for example, a cooling circuit 3 described later) is further provided, in which cooling water that exchanges heat with the internal combustion engine and its exhaust gas is circulated, the circulation flow path is provided with the container and a second heat exchanger (for example, an evaporator 56 described later) that exchanges heat between the organic medium and the cooling water of the cooling circuit in the first flow direction in this order, the rankine cycle circuit is provided with a bypass flow path (for example, a bypass flow path 60 described later) that connects between the first heat exchanger and the expansion valve among the circulation flow paths and between the container and the second heat exchanger, and a second pump (for example, a second pump 61 described later) that compresses the organic medium flowing in the first flow direction is provided in the bypass flow path.
(6) In this case, a motor generator (for example, a motor generator 57 described later) connected to the expander is preferably further provided.
(7) In this case, a motor generator (for example, a motor generator 57 described later) connected to the compression/expansion machine is preferably further provided.
(Effects of the invention)
(1) The thermal cycle system of the present invention includes a rankine cycle circuit in which an insulating organic medium is circulated. An expander, a first heat exchanger, and a first pump are provided in this order in a first flow direction in a circulation flow path of the rankine cycle circuit. A container through which an organic medium flows is provided between the first pump and the expander in the circulation flow path, and an electric storage device is provided in the container so as to be immersed in the organic medium. In this thermal cycle system, by circulating the organic medium in the first flow direction, a part of thermal energy obtained by heat exchange with the power storage device in the container can be discharged to the outside air, and the power storage device can be cooled. In particular, in the present invention, the power storage device is provided in the container so as to be immersed in the organic medium, and thus heat exchange can be directly performed between the power storage device and the organic medium, and therefore, the power storage device can be cooled uniformly and effectively. As described above, according to the thermal cycle system of the present invention, the power storage device can be cooled effectively by the rankine cycle circuit.
(2) The heat cycle system of the present invention includes a cooling circuit in which cooling water that exchanges heat with an internal combustion engine and its exhaust gas is circulated. In the present invention, a second heat exchanger that exchanges heat between the organic medium and the cooling water and a container that accommodates the power storage device are provided between the first pump and the expander in the circulation flow path. In this heat cycle system, the organic medium is circulated in the first flow direction, so that a part of the heat energy obtained by heat exchange with the cooling water of the internal combustion engine in the second heat exchanger and a part of the heat energy obtained by heat exchange with the power storage device in the container can be discharged to the outside air, and the internal combustion engine and the power storage device can be cooled. In the present invention, the circulating flow path is provided with a container for housing the power storage device and the second heat exchanger in this order along the first flow direction. Therefore, according to the present invention, as described above, since the power storage device having a low temperature region can be cooled before the cooling water of the internal combustion engine, both the power storage device and the internal combustion engine can be cooled effectively. In the present invention, the bypass flow path connects the first heat exchanger and the first pump and the container and the second heat exchanger in the circulation flow path, and the second pump for compressing the organic medium flowing in the first flow direction is provided in the bypass flow path. Therefore, according to the present invention, the rotation speed of the second pump is adjusted, whereby the amount of the organic medium flowing into the second heat exchanger via the container and the amount of the organic medium flowing into the second heat exchanger bypassing the container can be adjusted, and therefore, the temperature of the power storage device and the temperature of the internal combustion engine can be accurately adjusted.
(3) The thermal cycle system of the present invention includes a rankine cycle circuit in which an insulating organic medium is circulated. An expansion valve, a first heat exchanger, and a compressor are provided in this order in the second flow direction in the circulation flow path of the rankine cycle circuit. A container through which an organic medium flows is provided between the compressor and the expansion valve in the circulation flow path, and an electric storage device is provided in the container so as to be immersed in the organic medium. In this thermal cycle system, the organic medium is circulated in the second flow direction, and thereby a part of thermal energy obtained by heat exchange with outside air in the first heat exchanger is given to the power storage device, so that the power storage device can be heated. In particular, in the present invention, the power storage device is provided in the container so as to be immersed in the organic medium, and thus heat exchange can be directly performed between the power storage device and the organic medium, and therefore, the power storage device can be heated uniformly and efficiently. As described above, according to the thermal cycle system of the present invention, the power storage device can be efficiently heated by the rankine cycle circuit.
(4) In the present invention, a compression expander that compresses the organic medium in the second flow direction and decompresses the organic medium in the first flow direction is provided in the circulation flow path. In addition, an expansion valve for reducing the pressure of the organic medium in the second flow direction and a first pump for compressing the organic medium in the first flow direction are provided in parallel in the circulation flow path. In this thermal cycle system, the compression/expansion machine is used as a compressor to function and the organic medium is circulated in the second flow direction, whereby, as described above, a part of the thermal energy obtained by heat exchange with the outside air in the first heat exchanger can be given to the power storage device, and the power storage device can be heated. In this thermal cycle system, the compression expander is used as an expander to function, and the organic medium is circulated in the first flow direction, so that a part of thermal energy obtained by heat exchange with the power storage device in the container can be discharged to the outside air, and the power storage device can be cooled. As described above, according to the thermal cycle system of the present invention, the temperature of the power storage device can be effectively controlled by the rankine cycle circuit.
(5) The heat cycle system of the present invention includes a cooling circuit in which cooling water that exchanges heat with an internal combustion engine and its exhaust gas is circulated. In the present invention, a second heat exchanger for performing heat exchange between the organic medium and the cooling water and a container for housing the power storage device are provided between the first pump and the expander in the circulation flow path. In this thermal cycle system, the compression expander is used as an expander to function and the organic medium is circulated in the first flow direction, so that a part of thermal energy obtained by heat exchange with the cooling water in the second heat exchanger and a part of thermal energy obtained by heat exchange with the power storage device in the container can be discharged to the outside air to cool the internal combustion engine and the power storage device. In the present invention, the circulation flow path is provided with a container for housing the power storage device and a second heat exchanger in this order along the second flow direction. Therefore, according to the present invention, the organic medium is circulated in the first flow direction, and thereby the cooling of the power storage device and the cooling water of the internal combustion engine in the container can be performed in this order. In many vehicles equipped with an electric storage device and an internal combustion engine, the temperature range of the internal combustion engine is higher than the temperature range of the electric storage device. Therefore, in the present invention, since the power storage device having a low temperature region can be cooled before the cooling water of the internal combustion engine, both the power storage device and the internal combustion engine can be cooled effectively. In the present invention, the bypass flow path connects the first heat exchanger and the expansion valve in the circulation flow path to the container and the second heat exchanger, and a second pump for compressing the organic medium flowing in the first flow direction is provided in the bypass flow path. Therefore, according to the present invention, the rotation speed of the second pump is adjusted, whereby the amount of the organic medium flowing into the second heat exchanger via the container and the amount of the organic medium flowing into the second heat exchanger bypassing the container can be adjusted, and therefore, the temperature of the power storage device and the temperature of the internal combustion engine can be accurately adjusted.
(6) The thermal cycle system of the present invention further includes a motor generator connected to the expander. Thus, the pressure of the organic medium in the container can be controlled so that efficient heat exchange between the organic medium and the power storage device can be performed in the container. In addition, when the organic medium is circulated in the first flow direction to cool the cooling water of the power storage device and the internal combustion engine, the motor generator is used as a generator to function, whereby a part of the waste heat of the power storage device and a part of the waste heat of the internal combustion engine can be converted into electric energy to be recovered.
(7) The thermal cycle system of the present invention further includes a motor generator connected to the compression/expansion machine. As a result, as described above, the pressure of the organic medium in the container can be controlled, or a part of the waste heat of the power storage device and a part of the waste heat of the internal combustion engine can be converted into electric energy and recovered.
Drawings
Fig. 1 is a diagram showing a configuration of a thermal cycle system according to an embodiment of the present invention.
Fig. 2 is a table for explaining the contents of a plurality of control modes implemented according to the control apparatus.
Fig. 3A is a diagram showing the flow of the organic medium realized in the battery heating mode.
Fig. 3B is a diagram showing the flow of the organic medium realized in the battery cooling mode.
Fig. 3C is a diagram showing the flow of the organic medium implemented in the first and second engine cooling modes.
Fig. 3D is a diagram showing the flow of the organic medium implemented in the first and second hybrid cooling modes.
Fig. 4A is a mollier diagram of a thermal cycle implemented in a rankine cycle circuit when the battery heating mode is executed.
Fig. 4B is a mollier diagram of a thermal cycle implemented in the rankine cycle circuit when the battery cooling mode is executed.
Fig. 4C is a mollier diagram of a thermal cycle implemented in a rankine cycle circuit when executing the first and second engine cooling modes.
Fig. 4D is a mollier diagram of a thermal cycle implemented in a rankine cycle circuit when performing the first and second hybrid cooling modes.
Wherein, the reference numerals:
1 thermal circulation system
2 Engine (internal combustion engine)
3 Cooling Circuit
5 Rankine cycle circuit
7 Control device
50 Main circulation flow path
51 Compression expander (expander, compressor)
52 Condenser (first heat exchanger)
53 First pump
54 Electronic expansion valve (expansion valve)
55 Accumulator container (Container)
56 Evaporator (second heat exchanger)
57 Motor generator
60 Bypass flow path
61 Second Pump
81 Accumulator (accumulator)
Detailed Description
An embodiment of the present invention will be described below 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 provided with an internal combustion engine 2 (hereinafter referred to as "engine 2"), and preheats the engine 2 at the time of starting, or recovers and converts waste heat generated by the engine 2 after the preheating into electric energy.
The thermal cycle system 1 includes: a cooling circuit 3 that includes the engine 2 in a part of its path and in which cooling water circulates; a Rankine cycle circuit 5 in which an insulating organic medium is circulated; a control device 7 that operates the cooling circuit 3 and the rankine cycle circuit 5; and a battery 81 that can be discharged and charged.
The cooling circuit 3 includes a circulation passage 33 for cooling water, and a plurality of devices provided in the circulation passage 33, and the cooling water that exchanges heat with the engine 2 and its exhaust gas circulates in the circulation passage 33 for cooling water. More specifically, the cooling circuit 3 includes: a circulation flow path 33 including an evaporator 56 described later provided in the rankine cycle circuit 5; a first cooling water flow path 31 as a part of the circulation flow path 33; a second cooling water flow path 32 as a part of the circulation flow path 33; a first water pump 35 and a second water pump 36 for pumping cooling water through the circulation flow path 33; a heater core 37 for heating the cabin according to the cooling water flowing through the circulation flow path 33; 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.
The first cooling water flow path 31 is a flow path of 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 of 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. 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, the evaporator 56 is provided at a position downstream of the second cooling water flow path 32 and the heater core 37 and upstream of the first cooling water flow path 31.
The first water pump 35 is provided between the evaporator 56 and the first cooling water flow path 31 among the circulation flow paths 33. The first water pump 35 is operated in response to a control signal from the control device 7, and pumps the cooling water from the evaporator 56 side to the first cooling water flow path 31 side in the circulation flow path 33.
The bypass passage 34 is connected to the branch portion 38 between the first cooling water passage 31 and the second cooling water passage 32, and the evaporator 56, among the circulation passages 33. Therefore, a part of the cooling water flowing out of the first cooling water passage 31 flows back to the evaporator 56 or the first water pump 35 via the bypass passage 34.
The second water pump 36 is provided between the branching portion 38 in the circulation flow path 33 and the second cooling water flow path 32. The second water pump 36 is operated in response to a control signal from the control device 7, and pumps the cooling water from the first cooling water passage 31 side to the second cooling water passage 32 side in the circulation passage 33.
The rankine cycle circuit 5 includes: an annular main circulation flow path 50 in which an organic medium having a boiling point lower than that of cooling water and having insulation properties is circulated; the compressor-expander 51, the condenser 52, the first pump 53, the electronic expansion valve 54, the battery container 55, and the evaporator 56 are provided in the main circulation flow path 50; a bypass flow path 60 that bypasses a part of the plurality of devices provided in the main circulation flow path 50; and a second pump 61 provided in the bypass flow path 60.
The compression expander 51 is disposed between the evaporator 56 and the condenser 52 in the main circulation flow path 50. The compression expander 51 decompresses the organic medium flowing from the evaporator 56 side to the condenser 52 side in the main circulation flow path 50 (hereinafter, this flow direction is also referred to as "first flow direction F1"), and compresses the organic medium flowing from the condenser 52 side to the evaporator 56 side in the main circulation flow path 50 (hereinafter, this flow direction is also referred to as "second flow direction F2"). When the compressor/expander 51 rotates in the forward direction in which the organic medium flows in the first flow direction F1 in the main circulation flow path 50, the organic medium passing through the evaporator 56 is depressurized and supplied to the condenser 52. When the compressor/expander 51 performs the reverse rotation in which the organic medium flows in the second flow direction F2 in the main circulation flow path 50, the organic medium passing through the condenser 52 is compressed and supplied to the evaporator 56.
Further, a motor generator 57 is connected to the drive shaft 51a of the compressor/expander 51. The motor generator 57 is capable of transmitting electric power to the battery 81 in response to a control signal from the control device 7. Therefore, the motor generator 57 can rotate the compression/expansion machine 51 forward or backward by using the electric power supplied from the battery 81, or can generate electric power by using the mechanical energy recovered during the decompression of the organic medium in the compression/expansion machine 51, and can charge the battery 81 by using the generated electric power.
The condenser 52 is provided downstream of the compressor-expander 51 in the first flow direction F1 in the main circulation flow path 50. The condenser 52 includes an organic medium passage through which an organic medium flows and a fan that supplies outside air to the organic medium passage, and exchanges heat between the organic medium and the outside air.
The evaporator 56 is provided upstream of the compressor-expander 51 in the first flow direction F1 in the main circulation flow path 50. The evaporator 56 includes an organic medium flow path through which an organic medium flows and a cooling water flow path through which cooling water of the cooling circuit 3 flows, and exchanges heat between the organic medium and the cooling water.
The battery container 55 is provided upstream of the evaporator 56 in the first flow direction F1 in the main circulation flow path 50. The organic medium flows through the battery container 55. In addition, a battery 81 is provided inside the battery container 55 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.
A portion between the condenser 52 and the battery case 55 in the main circulation flow path 50 is branched into a first branch 50a and a second branch 50b. The first branch 50a is provided with a first pump 53, and the second branch 50b is provided with an electronic expansion valve 54. That is, the first pump 53 and the electronic expansion valve 54 are juxtaposed in the main circulation flow path 50.
The first pump 53 is provided on the downstream side of the condenser 52 and on the upstream side of the battery container 55 in the first flow direction F1 in the first branch 50 a. The first pump 53 operates according to a control signal from the control device 7 to compress the organic medium flowing in the first flow direction F1 in the first branch 50 a. The rotation speed control device 7 of the first pump 53 adjusts.
The electronic expansion valve 54 is provided in the second branch 50b on the downstream side of the battery container 55 and on the upstream side of the condenser 52 in the second flow direction F2. The electronic expansion valve 54 is a throttle valve, and decompresses the organic medium flowing in the second flow direction F2 in the second branch passage 50 b. The opening degree of the electronic expansion valve 54 is adjusted in response to a control signal from the control device 7.
According to the above description, the main circulation flow path 50 is provided with the compression expander 51, the condenser 52, the first pump 53, the battery container 55, and the evaporator 56 in this order along the first flow direction F1. In the main circulation flow path 50, a compression expander 51, an evaporator 56, a battery container 55, an electronic expansion valve 54, and a condenser 52 are provided in this order along the second flow direction F2.
The bypass flow path 60 connects the condenser 52 and the branches 50a,50b, and the battery container 55 and the evaporator 56 in the main circulation flow path 50. 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.
The second pump 61 operates in response to a control signal from the control device 7 to compress the organic medium flowing in the first flow direction F1 in the main circulation flow path 50. The rotation speed of the second pump 61 is adjusted according to the control device 7. That is, when the second pump 61 is turned ON (ON), a part of the organic medium flowing out of the condenser 52 in the first flow direction F1 bypasses the first pump 53, the electronic expansion valve 54, and the battery container 55, and flows back to the evaporator 56.
According to the thermal cycle system 1 described above, 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 are operated by the control device 7, whereby the rankine cycle circuit 5 can be operated in a plurality of control modes.
Fig. 2 is a table summarizing the contents of a plurality of control modes implemented by the control device 7.
As shown in fig. 2, the control modes are divided into the following 6 modes, namely: a battery heating mode that mainly heats the battery 81; a battery cooling mode that mainly cools the battery 81; a first engine cooling mode that recovers waste heat of the engine 2 and cools the engine 2 and its cooling water; a first hybrid cooling mode that recovers waste heat of the engine 2 and cools the battery 81 and the engine 2 and its cooling water; a second engine cooling mode that cools the engine 2 faster than the first engine cooling mode; and a second hybrid cooling mode that cools the battery 81 and the engine 2 and its cooling water faster than the first hybrid cooling mode. Among the above 6 control modes, the battery cooling mode, the first engine cooling mode, and the first hybrid cooling mode may be referred to as an exhaust heat recovery mode capable of recovering exhaust heat of the battery 81 and the engine 2.
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 classified into the following states: a non-recoverable waste heat state in which the cooling water temperature is lower than a predetermined recoverable waste heat temperature and waste heat of the engine 2 cannot be recovered in the rankine cycle circuit 5; a recoverable waste heat state in which the cooling water temperature is equal to or higher than the recoverable waste heat temperature and the waste heat of the engine 2 can be recovered in the rankine cycle circuit 5; and, an engine protection state is requested in which the cooling water temperature is set to be equal to or higher than the engine protection temperature that is set to be higher than the recoverable waste heat temperature, and the engine 2 and its cooling water need to be cooled rapidly. In the following, the description is given of the case where the state of the engine 2 is divided into the non-recoverable waste heat state, the recoverable waste heat state, and the requested engine protection state based on the temperature of the portion related to the engine 2, that is, the temperature of the cooling water of the engine 2, but the present invention is not limited to this. More specifically, the states of the engines 2 may be classified according to the temperature of the engines 2 instead of the cooling water temperature of the engines 2.
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 of the battery. More specifically, the state of the battery 81 is classified into the following states: requesting a battery heating state in which the battery temperature is lower than its optimal temperature and the battery 81 needs to be heated; and, a battery cooling state is requested, and the battery temperature is equal to or higher than the optimum temperature, and it is necessary to cool the battery 81.
As shown in fig. 2, when the state of the engine 2 is in the waste heat non-recoverable state and the state of the battery 81 is in the battery heating request state, the control device 7 operates the rankine cycle circuit 5 in the battery heating mode, and when the state of the engine 2 is in the waste heat non-recoverable state and the state of the battery 81 is in the battery cooling request state, the control device 7 operates the rankine cycle circuit 5 in the battery cooling mode. In addition, when the state of the engine 2 is in the waste heat recoverable state and the state of the battery 81 is in the battery heating request state, the control device 7 operates the rankine cycle circuit 5 in the first engine cooling mode, and when the state of the engine 2 is in the waste heat recoverable state and the state of the battery 81 is in the battery cooling request state, the control device 7 operates the rankine cycle circuit 5 in the first hybrid cooling mode. In addition, the control device 7 operates the rankine cycle circuit 5 in the second engine cooling mode when the state of the engine 2 is in the engine-protected-request state and the state of the battery 81 is in the battery-heated-request state, and operates the rankine cycle circuit 5 in the second hybrid cooling mode when the state of the engine 2 is in the engine-protected-request state and the state of the battery 81 is in the battery-cooled-request state. Details of each control mode will be described below.
< Battery heating mode >)
Fig. 3A is a diagram showing the flow of the organic medium implemented in the rankine cycle circuit 5 when the battery heating mode is executed. As indicated by the thick arrow in fig. 3A, in the battery heating mode, the control device 7 operates the rankine cycle circuit 5 such that the organic medium circulates in the second flow direction F2 in the order of the compression expander 51, the evaporator 56, the battery container 55, the electronic expansion valve 54, and the condenser 52. More specifically, in the battery heating mode, the control device 7 turns OFF (OFF) the first pump 53 and the second pump 61, and supplies electric power to the motor generator 57 from the battery 81, thereby reversely rotating the compression expander 51 by the motor generator 57, and opening the electronic expansion valve 54. In the battery heating mode, the rankine cycle circuit 5 is operated in the above-described manner according to the control device 7, whereby the thermal cycle shown in fig. 4A is realized.
Fig. 4A is a mollier diagram showing a thermal cycle implemented 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 indicated by a thin broken line, and the saturated liquid line of the organic medium is indicated by a thin dot-dash line. That is, the organic medium is in a superheated steam state on the right side of the saturated steam line, in a supercooled liquid 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 performed, the organic medium is compressed by the compression expander 51 and supplied to the evaporator 56 and the battery container 55 in a superheated steam state. The organic medium compressed by the compression expander 51 is cooled by heat exchange with the cooling water and the battery 81 while flowing through the evaporator 56 and the battery container 55, and is supplied to the electronic expansion valve 54 in a supercooled liquid state. The organic medium supplied to the electronic expansion valve 54 is depressurized according to the electronic expansion valve 54, and is supplied to the condenser 52 in a supercooled liquid state or a mixed phase state. The organic medium supplied from the electronic expansion valve 54 is heated by heat exchange with the outside air while passing through the condenser 52, and is supplied to the compression expander 51 in a superheated vapor state. Therefore, when the battery heating mode is performed, a part of heat energy due to the outside air is supplied to the battery 81, whereby the temperature of the battery 81 rises.
< Battery Cooling mode >)
Fig. 3B is a diagram showing the flow of the organic medium implemented in the rankine cycle circuit 5 when the battery cooling mode is executed. As indicated by the thick arrow in fig. 3B, in the battery cooling mode, the control device 7 operates the rankine cycle circuit 5 such that the organic medium circulates in the first flow direction F1 in the order of the first pump 53, the battery container 55, the evaporator 56, the compression expander 51, and the condenser 52. More specifically, in the battery heating mode, the control device 7 turns off the second pump 61, turns off the electronic expansion valve 54, and turns on the first pump 53, causing the compressor-expander 51 to rotate in the forward direction. In the battery cooling mode, the rankine cycle circuit 5 is operated in the above-described manner according to the control device 7, whereby the thermal cycle shown in fig. 4A is realized.
Fig. 4B is a mollier diagram showing a thermal cycle implemented in the rankine cycle circuit 5 when the battery cooling mode is executed. As shown in fig. 4B, when the battery cooling mode is performed, the organic medium is compressed by the first pump 53 and supplied to the battery container 55 and the evaporator 56 in a supercooled liquid state. The organic medium compressed by the first pump 53 is heated by heat exchange with the battery 81 and the cooling water while flowing through the battery container 55 and the evaporator 56, and is supplied to the compression expander 51 in the form of superheated steam. The organic medium flowing out of the evaporator 56 in the form of superheated steam is depressurized in the compression expander 51 and supplied to the condenser 52 in the form 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 a supercooled liquid state. Therefore, when the battery cooling mode is performed, a part of the thermal energy of the battery 81 is discharged to the outside air, and thereby the temperature of the battery 81 is lowered. Here, in the battery cooling mode, the control device 7 operates the first pump 53 and the motor generator 57 so that the organic medium is maintained in a boiling state in the battery container 55, in other words, so that the battery 81 is cooled by latent heat of the organic medium in the battery container 55.
Herein, the boiling point of the organic medium in the battery container 55 varies according to the amount of the organic medium in the battery container 55 and the variation of the pressure. Therefore, in the battery cooling mode, the control device 7 controls the amount and pressure of the organic medium in the battery container 55 using 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 that is specified around the optimal temperature of the battery 81. More specifically, the control device 7 calculates a target amount and a 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, adjusts the rotation speed of the first pump 53 so that the amount of the organic medium in the battery container 55 becomes the target amount, and further operates the motor generator 57 as a generator, an idle state, or a motor so that the pressure of the organic medium in the battery container 55 becomes the target pressure.
< First Engine Cooling mode >)
Fig. 3C is a diagram showing the flow of the organic medium implemented in the rankine cycle circuit 5 when the first and second engine cooling modes are executed. As indicated by the thick arrow in fig. 3C, in the first engine cooling mode, the control device 7 operates the rankine cycle circuit 5 such that the organic medium circulates in the first flow direction F1 in the order of the second pump 61, the evaporator 56, the compression expander 51, and the condenser 52. More specifically, in the first engine cooling mode, the control device 7 turns off the first pump 53, turns off the electronic expansion valve 54, and turns on the second pump 61, causing the compressor-expander 51 to rotate in the forward direction. In the first engine cooling mode, the rankine cycle circuit 5 is operated in the manner described above according to the control device 7, whereby the thermal cycle shown in fig. 4C is realized.
Fig. 4C is a mollier diagram showing a thermal cycle implemented 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 performed, the organic medium is compressed by the second pump 61 and supplied to the evaporator 56 in a supercooled liquid state. The organic medium compressed by the second pump 61 is heated by heat exchange with the cooling water while passing through the evaporator 56, and is supplied to the compression expander 51 in a superheated vapor state. The organic medium flowing out of the evaporator 56 in the form of superheated steam is depressurized in the compression expander 51 and supplied to the condenser 52 in the form 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 a supercooled liquid state. Here, in the first engine cooling mode, the control device 7 uses mechanical energy generated in the drive shaft 51a during decompression of the organic medium in the compression/expansion machine 51 to generate electric power for the motor generator 57, and uses the electric power thus obtained to charge the battery 81. Therefore, when the first engine cooling mode is executed, a part of the heat energy of the cooling water is discharged to the outside air and converted into electric energy by the motor generator 57 to be recovered, whereby the temperatures of the cooling water and the engine 2 are lowered. Here, in the first engine cooling mode, the control device 7 operates the second pump 61 and the motor generator 57 so that the organic medium maintains a boiling state in the evaporator 56, in other words, so that the cooling water is cooled by latent heat of the organic medium in the evaporator 56.
Herein, the boiling point of the organic medium in the evaporator 56 varies according to the amount of the organic medium in the evaporator 56 and the variation of the pressure. Therefore, in the first engine cooling mode, the control device 7 controls the amount and pressure of the organic medium in the evaporator 56 using the second pump 61 and the motor generator 57 so that the boiling point of the organic medium in the evaporator 56 is maintained at the target temperature of the cooling water. More specifically, the control device 7 calculates a target amount and a target pressure of the organic medium in the evaporator 56 such that the boiling point of the organic medium in the evaporator 56 is maintained at the target temperature, adjusts the rotation speed of the second pump 61 such that the amount of the organic medium in the evaporator 56 becomes the target amount, and adjusts the power generation amount of the motor generator 57 such that the pressure of the organic medium in the evaporator 56 becomes the target pressure.
As described above, in the first engine cooling mode, since the control device 7 operates the motor generator 57 as a generator, the pressure in the evaporator 56 is higher than in the battery heating mode and the battery cooling mode described above (refer to fig. 2).
< First hybrid Cooling mode >)
Fig. 3D is a diagram showing the flow of the organic medium implemented in the rankine cycle circuit 5 when the first and second hybrid cooling modes are performed. As indicated by the thick arrow in fig. 3D, in the first hybrid cooling mode, the control device 7 operates the rankine cycle circuit 5 so that the organic medium circulates along two circulation paths, i.e., a first circulation path in which the organic medium is configured in the order of the first pump 53, the battery container 55, the evaporator 56, the compression expander 51, and the condenser 52 in the first flow direction F1, and a second circulation path in which the organic medium is configured in the order of the second pump 61, the evaporator 56, the compression expander 51, and the condenser 52 in the first flow direction F1. More specifically, in the first hybrid cooling mode, the control device 7 closes the electronic expansion valve 54, and opens the first pump 53 and the second pump 61, causing the compressor-expander 51 to rotate in the forward direction. In the first hybrid cooling mode, the rankine cycle circuit 5 is operated in the above-described manner according to the control device 7, whereby the thermal cycle 4 shown in fig. 4D is realized.
Fig. 4D is a mollier diagram showing a thermal cycle implemented in the rankine cycle circuit 5 when the first and second hybrid cooling modes are executed. As shown in fig. 4D, when the first hybrid cooling mode is performed, the organic medium is compressed by the first pump 53 and supplied to the battery container 55 in a supercooled liquid state. The organic medium compressed by the first pump 53 is heated by heat exchange with the battery 81 while flowing through the battery container 55, and is supplied to the evaporator 56 in a superheated steam or boiling state. The organic medium flowing out of the battery container 55 in a superheated vapor or boiling state is further heated by heat exchange with the cooling water while passing through the evaporator 56, and is supplied to the compression expander 51 in a superheated vapor state. The organic medium flowing out of the evaporator 56 in the form of superheated steam is depressurized in the compression expander 51 and supplied to the condenser 52 in the form 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 a supercooled liquid state. In addition, as described above, in the first hybrid cooling mode, the second pump 61 is turned on in addition to the first pump 53. Accordingly, a part of the organic medium flowing out from the condenser 52 in a supercooled liquid state is compressed by the second pump 61, bypasses the first pump 53 and the battery container 55, and is supplied to the evaporator 56 in a supercooled liquid state.
Here, in the first hybrid cooling mode, the control device 7 uses mechanical energy generated on the drive shaft 51a during decompression of the organic medium in the compression expander 51 to generate electric power for the motor generator 57, and uses the electric power thus obtained to charge the battery 81. Therefore, when the first hybrid cooling mode is executed, a part of the heat energy of the battery 81 and a part of the heat energy of the cooling water are discharged to the outside air, and at the same time, are recovered by being converted into electric energy by the motor generator 57, whereby the temperatures of the battery 81, the cooling water, and the engine 2 are lowered.
Here, in the first hybrid cooling mode, the control device 7 operates the first pump 53, the second pump 61, and the motor generator 57 such that the organic medium flows out of the battery container 55 at a temperature slightly lower than the boiling point, and such that the organic medium is maintained in a boiling state in the evaporator 56, in other words, such that the battery 81 is cooled by sensible heat of the organic medium in the battery container 55, and the cooling water is cooled by latent heat of the organic medium in the evaporator 56.
As described above, the boiling point of the organic medium in the evaporator 56 varies according to the amount of the organic medium in the evaporator 56 and the variation of the pressure. Therefore, in the first hybrid cooling mode, the control device 7 controls the amount and pressure of the organic medium in the evaporator 56 using the first pump 53, the second pump 61, and the motor generator 57 so that the temperature of the organic medium flowing out of the battery container 55 is slightly lower than the boiling point, and so that the boiling point of the organic medium in the evaporator 56 is maintained at the target temperature of the cooling water. More specifically, the control device 7 calculates a target amount of the organic medium in the battery container 55 and a target amount and a target pressure of the organic medium in the evaporator 56, so that the organic medium flows out of 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, adjusts the rotation speed of the first pump 53 so that the amount of the organic medium in the battery container 55 becomes the target amount, adjusts the rotation speed of the second pump 61 so that the amount of the organic medium in the evaporator 56 becomes the target amount, and adjusts the power generation amount of the motor generator 57 so that the pressure of the organic medium in the evaporator 56 becomes the target pressure.
As described above, in the first hybrid cooling mode, since the control device 7 operates the motor generator 57 as a generator, the pressure in the evaporator 56 is higher than in the battery heating mode and the battery cooling mode described above (refer to fig. 2).
< Second Engine Cooling mode >)
As indicated by the thick arrow in fig. 3C, in the second engine cooling mode, the control device 7 operates the rankine cycle circuit 5 in such a manner that the organic medium circulates in the first flow direction F1 in the order of the second pump 61, the evaporator 56, the compression expander 51, and the condenser 52, as in the first engine cooling mode described above. Thus, in the second engine cooling mode, as shown in fig. 4C, the same thermal cycle qualitatively as in the first engine cooling mode is achieved.
As described with reference to fig. 2, the control device 7 executes the first engine cooling mode in the case where the battery 81 is in the battery heating request state and the cooling water temperature is higher than or equal to the recoverable waste heat temperature and lower than the engine protection temperature, and executes the second engine cooling mode in the case where the battery 81 is in the battery heating request state and the cooling water temperature is higher than or equal to the engine protection temperature and rapid cooling of the engine 2 and its cooling water is required. Therefore, in the second engine cooling mode, the control device 7 sets the motor generator 57 to an idle state or supplies the electric power of the battery 81 to the motor generator 57, and drives the compressor-expander 51 with the motor generator 57 so that the cooling water can be cooled quickly. Thus, in the second engine cooling mode, the pressure within the evaporator 56 is lower than in the first engine cooling mode and the first hybrid cooling mode described above (refer to fig. 2).
< Second Mixed Cooling mode >)
As shown by the thick arrow in fig. 3D, in the second hybrid cooling mode, the control device 7 operates the rankine cycle circuit 5 in the same manner as in the first hybrid cooling mode described above so that the organic medium circulates along two circulation flow paths, i.e., a first circulation flow path in which the organic medium is configured in the order of the first pump 53, the battery container 55, the evaporator 56, the compressor-expander 51, and the condenser 52 in the first flow direction F1, and a second circulation flow path in which the second pump 61, the evaporator 56, the compressor-expander 51, and the condenser 52 are configured in the order of the second pump 61, the evaporator 56, the compressor-expander 51, and the condenser 52. Thus, in the second hybrid cooling mode, as shown in fig. 4D, the same thermal cycle qualitatively as that of the first hybrid cooling mode is achieved.
As described with reference to fig. 2, the control device 7 executes the first hybrid cooling mode in the case where the battery 81 is in the battery cooling request state and the cooling water temperature is higher than or equal to the recoverable waste heat temperature and lower than the engine protection temperature, and executes the second hybrid cooling mode in the case where the battery 81 is in the battery cooling request state and the cooling water temperature is higher than or equal to the engine protection temperature and rapid cooling of the engine 2 and its cooling water is required. Therefore, in the second hybrid cooling mode, the control device 7 sets the motor generator 57 to an idle state or supplies the electric power of the battery 81 to the motor generator 57, and drives the compressor-expander 51 with the motor generator 57 so that the cooling water can be cooled quickly. Thus, in the second hybrid cooling mode, the pressure in the evaporator 56 is lower than in the first engine cooling mode and the first hybrid cooling mode described above (refer to fig. 2).
According to the thermal cycle system 1 of the present embodiment, the following effects are achieved.
(1) The thermal cycle system 1 includes: a cooling circuit 3 in which cooling water that exchanges heat with the engine 2 and its exhaust gas is circulated; and a Rankine cycle circuit 5 in which an insulating organic medium is circulated. The main circulation flow path 50 of the rankine cycle circuit 5 is provided with a compression expander 51, a condenser 52, and a first pump 53 in this order along the first flow direction F1. Further, an evaporator 56 for exchanging heat between the organic medium and the cooling water and a battery container 55 in which the organic medium flows are provided between the first pump 53 and the compression/expansion machine 51 in the main circulation flow path 50, and a battery 81 is provided in the battery container 55 so as to be immersed in the organic medium. In the heat cycle system 1, the organic medium is circulated in the first flow direction F1, and thereby a part of the heat energy obtained by heat exchange with the cooling water of the engine 2 in the evaporator 56 and a part of the heat energy obtained by heat exchange with the battery 81 in the battery case 55 are discharged to the outside air, whereby the engine 2 and the battery 81 can be cooled. In particular, in the thermal cycle system 1, the battery 81 is provided in the battery container 55 so as to be immersed in the insulating organic medium, and thus heat exchange can be directly performed between the battery 81 and the organic medium, and therefore, the battery 81 can be cooled uniformly and effectively. As described above, according to the heat cycle system 1, the battery 81 can be effectively cooled by the rankine cycle circuit 5 that can exchange heat with the cooling water of the engine 2.
(2) In the thermal cycle system 1, a battery container 55 that houses a battery 81 and an evaporator 56 are provided in this order in the main cycle flow path 50 along the first flow direction F1. Therefore, according to the thermal cycle system 1, since the battery 81 having a low temperature region can be cooled before the cooling water of the engine 2, both the battery 81 and the engine 2 can be cooled effectively. In the thermal cycle system 1, the bypass flow path 60 connects the condenser 52 and the first pump 53 in the main circulation flow path 50 and the battery container 55 and the evaporator 56, and the bypass flow path 60 is provided with the second pump 61 for compressing the organic medium flowing in the first flow direction F1. Therefore, according to the thermal cycle system 1, the rotation speed of the second pump 61 is adjusted, whereby the amount of the organic medium flowing into the evaporator 56 via the battery container 55 and the amount of the organic medium flowing into the evaporator 56 bypassing the battery container 55 can be adjusted, and therefore, the temperature of the battery 81 and the temperature of the engine 2 can be accurately adjusted.
(3) The thermal cycle system 1 includes: a cooling circuit 3 in which cooling water that exchanges heat with the engine 2 and its exhaust gas is circulated; and a Rankine cycle circuit 5in which an insulating organic medium is circulated. The main circulation flow path 50 of the rankine cycle circuit 5 is provided with an electronic expansion valve 54, a condenser 52, and a compression/expansion machine 51 in this order along the second flow direction F2. Further, an evaporator 56 for exchanging heat between the organic medium and the cooling water and a battery container 55 in which the organic medium flows are provided between the electronic expansion valve 54 and the compression expander 51 in the main circulation flow path 50, and a battery 81 is provided in the battery container 55 so as to be immersed in the organic medium. In the thermal cycle system 1, the organic medium is circulated in the second flow direction F2, and thereby a part of thermal energy obtained by heat exchange with the outside air in the condenser 52 is given to the battery 81, so that the battery 81 can be heated. In particular, in the thermal cycle system 1, the battery 81 is provided in the battery container 55 so as to be immersed in the insulating organic medium, and thus heat exchange can be directly performed between the battery 81 and the organic medium, and therefore, the battery 81 can be heated uniformly and efficiently. As described above, according to the heat cycle system 1, the battery 81 can be efficiently heated by the rankine cycle circuit 5 that can exchange heat with the cooling water of the engine 2.
(4) In the thermal cycle system 1, a compression expander 51 that compresses the organic medium in the second flow direction F2 and decompresses the organic medium in the first flow direction F1 is provided in the main circulation flow path 50. In the main circulation flow path, an electronic expansion valve 54 for depressurizing the organic medium in the second flow direction F2 and a first pump 53 for compressing the organic medium in the first flow direction F1 are provided in parallel. In this thermal cycle system 1, the compressor-expander 51 functions as a compressor and circulates the organic medium in the second flow direction F2, whereby a part of the thermal energy obtained by exchanging heat with the outside air in the condenser 52 can be given to the battery 81 as described above, and the battery 81 can be heated. In the thermal cycle system 1, the compression/expansion machine 51 functions as an expansion machine, and the organic medium is circulated in the first flow direction F1, whereby a part of thermal energy obtained by heat exchange with the cooling water in the evaporator 56 and a part of thermal energy obtained by heat exchange with the battery 81 in the battery case 55 can be discharged to the outside air, and the engine 2 and the battery 81 can be cooled. As described above, according to the thermal cycle system 1, the temperature control of the engine 2 and the temperature control of the battery 81 can be effectively performed according to the rankine cycle circuit 5.
(5) In the thermal cycle system 1, a battery container 55 that houses a battery 81 and an evaporator 56 are provided in this order in the main circulation flow path 50 along the second flow direction F2. Therefore, according to the thermal cycle system 1, the organic medium is circulated in the first flow direction F1, and thereby the battery 81 and the cooling water of the engine 2 in the battery case 55 can be cooled in this order. In a vehicle in which the battery 81 and the engine 2 are mounted, the temperature range of the engine 2 is often higher than that of the battery 81. Therefore, in the thermal cycle system 1, since the battery 81 having a low temperature region can be cooled before the cooling water of the engine 2, both the battery 81 and the engine 2 can be cooled effectively. In the thermal cycle system 1, the bypass flow path 60 connects the condenser 52 and the electronic expansion valve 54 in the main circulation flow path 50 and the battery container 55 and the evaporator 56, and a second pump 61 is provided in the bypass flow path 60 to compress the organic medium flowing in the first flow direction F1. Therefore, according to the thermal cycle system 1, the rotation speed of the second pump 61 is adjusted, whereby the amount of the organic medium flowing into the evaporator 56 via the battery container 55 and the amount of the organic medium flowing into the evaporator 56 bypassing the battery container 55 can be adjusted, and therefore, the temperature of the battery 81 and the temperature of the engine 2 can be accurately adjusted.
(6) The thermal cycle system 1 further includes a motor generator 57 connected to the compression/expansion machine 51. Thereby, the pressure of the organic medium in the battery container 55 can be controlled so that efficient heat exchange between the organic medium and the battery 81 is performed in the battery container 55. When the organic medium is circulated in the first flow direction F1 and the cooling water of the battery 81 and the engine 2 is cooled, the motor generator 57 is used as a generator to function, and a part of the waste heat of the battery 81 and a part of the waste heat of the engine 2 can be converted into electric energy to be recovered.
While the above description has been given of the embodiment of the present invention, the present invention is not limited to this. The configuration of the detail part may be changed as appropriate within the scope of the gist of the present invention.

Claims (4)

1. A thermal cycle system is provided with: a cooling circuit in which cooling water that exchanges heat with the internal combustion engine and its exhaust gas is circulated; and a rankine cycle circuit in which an insulating organic medium is circulated, wherein the thermal cycle system is characterized in that:
In the circulation flow path of the rankine cycle circuit, along the first flow direction, there are sequentially provided: an expander that decompresses an organic medium flowing in the first flow direction; a first heat exchanger that performs heat exchange between an organic medium and outside air; and a first pump for compressing the organic medium flowing in the first flow direction;
And, between the first pump and the expander in the circulation flow path, there are sequentially provided: a container in which an organic medium flows; and a second heat exchanger for exchanging heat between the organic medium and the cooling water of the cooling circuit,
The rankine cycle circuit includes: a bypass flow path connecting between the first heat exchanger and the first pump and between the tank and the second heat exchanger in the circulation flow path; and a second pump provided in the bypass flow path, the second pump compressing the organic medium flowing in the first flow direction,
The container is provided with an electric storage device so as to be immersed in an organic medium.
2. A thermal cycle system is provided with: a cooling circuit in which cooling water that exchanges heat with the internal combustion engine and its exhaust gas is circulated; and a rankine cycle circuit in which an insulating organic medium is circulated, wherein the thermal cycle system is characterized in that:
In the circulation flow path of the rankine cycle circuit, along the second flow direction, there are sequentially provided: an expansion valve for depressurizing the organic medium flowing in the second flow direction; a first heat exchanger that performs heat exchange between an organic medium and outside air; a compression expander that compresses an organic medium flowing in the second flow direction and decompresses the organic medium flowing in a first flow direction opposite to the second flow direction; and a first pump which is disposed in parallel with the expansion valve and compresses the organic medium flowing in the first flow direction,
And, between the compressor and the expansion valve in the circulation flow path, in the first flow direction, there are sequentially provided: a container in which an organic medium flows; and a second heat exchanger for exchanging heat between the organic medium and the cooling water of the cooling circuit,
The rankine cycle circuit includes: a bypass flow path connecting between the first heat exchanger and the expansion valve and between the tank and the second heat exchanger in the circulation flow path; and a second pump for compressing the organic medium flowing in the first flow direction,
The container is provided with an electric storage device so as to be immersed in an organic medium.
3. The thermal cycle system according to claim 1, further comprising a motor generator connected to the expander.
4. The thermal cycle system according to claim 2, further comprising a motor generator connected to the compression expander.
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