JP7057323B2 - Thermal cycle system - Google Patents

Description

The present invention relates to a thermodynamic cycle system. More specifically, the present invention relates to a thermodynamic cycle system including a cooling circuit of an internal combustion engine and a Rankine cycle circuit.

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). ..

Japanese Unexamined Patent Publication No. 2006-118754

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, in the past, how to combine the battery temperature control system and the Rankine cycle circuit in order to efficiently recover both the waste heat of the internal combustion engine and control the temperature of the battery has been sufficiently studied. There wasn't.

An object of the present invention is to provide a thermal cycle system capable of efficiently performing both waste heat recovery of an internal combustion engine and temperature control of a battery.

(1) The heat cycle system according to the present invention (for example, the heat cycle systems 1 and 1A described later) is an internal combustion engine cooling 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 circuit (for example, the engine cooling circuit 3 described later) and a Rankin cycle circuit in which an insulating organic medium circulates (for example, the Rankin cycle circuits 5 and 5A described later) are provided, and the Rankin cycle circuit includes the circuit (for example, the Rankin cycle circuit 5 and 5A described later). In the circulation flow path (for example, the main circulation flow path 50 and 50A described later), an expander (for example, an expander 55 and a compression expander 59 described later) for reducing the pressure of the organic medium in order along the flow of the organic medium is provided. , Heat between the condenser that cools the organic medium by the outside air (for example, the condenser 56 described later) and the organic medium and the electric device (for example, the battery 81 described later) or the electric device and the heat exchangeable working medium. The first heat exchange unit (for example, the chiller 52 and the battery container 65 described later) for exchanging heat and the second heat exchange unit (for example, the heat exchanger 53 described later) for exchanging heat between the organic medium and the cooling water. Evaporator 54) and is provided.

(2) In this case, the heat cycle system further includes a control device (for example, control devices 7 and 7A described later) for operating the Rankine cycle circuit, and the condenser and the first heat in the circulation flow path. A pump for compressing an organic medium (for example, a first pump 51 and a second pump 64, which will be described later) is provided between the exchange unit and the control device, wherein the electric device or the operating medium is the first heat exchange unit. It is preferable to operate the pump so that the cooling water is cooled by the sensible heat of the organic medium and the cooling water is cooled by the latent heat of the organic medium in the second heat exchange section.

(3) In this case, the heat cycle system includes an electric device cooling circuit (for example, a battery cooling circuit 4 described later) in which an operating medium that exchanges heat with the electric device circulates, and circulates in the electric device cooling circuit. It is preferable that the working medium can exchange heat with the organic medium in the first heat exchange unit.

(4) In this case, it is preferable that the thermodynamic cycle system further includes a motor generator (for example, a motor generator 57 described later) connected to the expander.

(1) The thermal cycle system of the present invention includes an internal combustion engine cooling circuit in which cooling water that exchanges heat with the internal combustion engine and its exhaust is circulated, and a Rankine cycle circuit in which an insulating organic medium circulates. Further, in the circulation flow path of the Rankin cycle circuit, an expander that depressurizes the organic medium in order along the flow of the organic medium, a condenser that cools the organic medium by the outside air, an organic medium and an electric device, or an electric device thereof. A first heat exchange unit for heat exchange between the heat exchangeable working medium and a second heat exchange unit for heat exchange between the organic medium and the cooling water are provided. For example, in a vehicle equipped with both an electric device and an internal combustion engine, the temperature range of the internal combustion engine is higher than that of the electric device in many situations. Therefore, in the present invention, the first heat exchange unit that exchanges heat with the electric device having a lower temperature zone than the internal combustion engine or its operating medium is more condensate than the second heat exchange unit that exchanges heat with the cooling water of the internal combustion engine. Install closer to. Therefore, according to the present invention, by circulating the organic medium in the order of the expander, the condenser, the first heat exchange section, and the second heat exchange section, the electric device having a lower temperature zone in the first heat exchange section or After cooling the working medium, the cooling water of the internal combustion engine having a higher temperature range can be further cooled by the organic medium heated by the heat exchange in the first heat exchange section. Therefore, according to the present invention, the organic medium circulating in the Rankine cycle circuit can efficiently cool both the electric device and the internal combustion engine having different temperature zones.

(2) In the heat cycle system of the present invention, in the control device, the electric device or its operating medium is cooled by the sensible heat of the organic medium in the first heat exchange section, and the cooling water of the internal combustion engine is organic in the second heat exchange section. Operate the pump to be cooled by the latent heat of the medium. Here, when cooling by the latent heat of the organic medium, the temperature of the organic medium can be kept constant at a predetermined target temperature, so that the cooling can be performed more efficiently than the case of cooling by sensible heat. Therefore, according to the present invention, both the electric device and the internal combustion engine having a higher temperature range can be efficiently cooled by the organic medium circulating in the circulation flow path.

(3) The heat cycle system of the present invention includes an electric device cooling circuit in which an operating medium that exchanges heat with an electric device circulates. Further, in the present invention, the working medium circulating in the cooling circuit of the electric device can exchange heat with the organic medium in the first heat exchange unit. Thereby, for example, by stopping the circulation of the working medium in the electric device cooling circuit while circulating the organic medium in the Rankine cycle circuit, only the internal combustion engine can be positively cooled.

(4) The thermodynamic cycle system of the present invention further includes a motor generator connected to an inflator. As a result, the motor generator functions as a generator while circulating the organic medium in the order of the expander, the condenser, the first heat exchange section, and the second heat exchange section, thereby causing heat in the first and second heat exchange sections. In the process of depressurizing the organic medium heated by exchange in the expander, a part of the waste heat of the electric device and the internal combustion engine can be recovered as electric energy. Further, according to the heat cycle system of the present invention, the first heat exchange unit uses a motor generator so that effective heat exchange between the organic medium and the electric device or the cooling water is performed in the first and second heat exchange units. And the pressure of the organic medium in the second heat exchange section can also be controlled.

It is a figure which shows the structure of the thermal cycle system which concerns on 1st Embodiment of this invention. It is a figure which shows the flow of the organic medium realized in the hybrid cooling mode. It is a Moriel diagram of the thermal cycle realized in the Rankine cycle circuit when the hybrid cooling mode is executed. It is a figure which shows the structure of the thermal cycle system which concerns on 2nd Embodiment of this invention. It is a figure which shows the flow of the organic medium realized in the hybrid cooling mode. It is a Moriel diagram of the thermal cycle realized in the Rankine cycle circuit when the hybrid cooling mode is executed.

<First Embodiment>
Hereinafter, the first 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 thermodynamic cycle system 1 is mounted on a hybrid vehicle whose drive source is an internal combustion engine 2 (hereinafter referred to as "engine 2") and a drive motor (not shown).

The thermal cycle system 1 is insulated from an engine cooling circuit 3 in which cooling water for cooling the engine 2 circulates, a battery cooling circuit 4 in which an operating medium for cooling the battery 81 that supplies electric power to the drive motor described above circulates, and the battery cooling circuit 4. It includes a Rankine cycle circuit 5 in which an organic medium circulates, and a control device 7 for operating the engine cooling circuit 3, the battery cooling circuit 4, and the Rankine cycle circuit 5.

The engine 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 is circulated, and a plurality of devices provided in the circulation flow path 33. More specifically, the engine cooling circuit 3 is a circulation flow path 33 including a heat exchanger 53 and an evaporator 54, which will be described later, provided in the Rankine cycle circuit 5, and a part of the circulation flow path 33. The first cooling water flow path 31, the second cooling water flow path 32 that is a part of the circulation flow path 33, the first water pump 35 and the second water pump 36 that pump the cooling water in the circulation flow path 33, and the circulation flow. It includes a heater core 37 that heats the cabin with cooling water flowing through the passage 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 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 cooling water flow path that promotes heat exchange between the cooling water and the exhaust. The second cooling water flow path 32 is formed in the exhaust pipe on the downstream side of the exhaust purification catalyst 21. The heat exchanger 53 and the evaporator 54 are located on the downstream side of the second cooling water flow path 32 and the heater core 37 when the cooling water is circulated by the first water pump 35 and the second water pump 36 in the annular circulation flow path 33. It is provided at a position such that it is on the upstream side of the first cooling water flow path 31.

The first water pump 35 is provided between the heat exchanger 53 and the evaporator 54 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 heat exchanger 53 and the evaporator 54 side to the first cooling water flow path 31 side in the circulation flow path 33.

The bypass flow path 34 is a second circulation flow path 33 between the first branch portion 38 between the first cooling water flow path 31 and the second cooling water flow path 32, and the heat exchanger 53 and the evaporator 54. Connect to the branch portion 39. Therefore, a part of the cooling water flowing out from the first cooling water flow path 31 is returned to the heat exchanger 53 through the bypass flow path 34.

The second water pump 36 is provided between the first 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.

The battery cooling circuit 4 is composed of a circulation flow path 41 of the working medium in which the working medium that exchanges heat with the battery 81 circulates, and a plurality of devices provided in the circulation flow path 41. More specifically, the battery cooling circuit 4 includes a circulation flow path 41 including a chiller 52, which will be described later, provided in the Rankine cycle circuit 5, a heat exchanger 42 provided in the circulation flow path 41, and a second. A pump 43 and a battery container 45 are provided. In the following, a case where an insulating fluid such as oil or an organic medium is used as the working medium circulating in the circulation flow path 41 will be described, but the present invention is not limited to this. As the working medium that circulates in the circulation flow path 41, cooling water that circulates in the circulation flow path 33 of the engine cooling circuit 3 may be used.

The circulation flow path 41 includes a chiller 52, a heat exchanger 42 that exchanges heat between the outside air and the working medium, a second pump 43 that compresses the working medium, and a battery in the clockwise order in FIG. A battery container 45 for accommodating 81 is provided.

The second pump 43 is provided between the heat exchanger 42 and the battery container 45 in the circulation flow path 41. The second pump 43 is provided in the circulation flow path 41 with the heat exchanger 42 side as the inlet and the battery container 45 side as the outlet. The second pump 43 operates in response to a control signal from the control device 7, compresses the working medium supplied from the heat exchanger 42, and supplies the working medium to the battery container 45. The rotation speed of the second pump 43 is adjusted by the control device 7.

The heat exchanger 42 is provided between the chiller 52 and the second pump 43 in the circulation flow path 41. The heat exchanger 42 includes a working medium flow path through which the working fluid flows and a fan for supplying outside air to the working medium flow path, and heat exchanges between the working medium and the outside air.

The battery container 45 is provided between the second pump 43 and the chiller 52 in the circulation flow path 41. A working medium passes through the inside of the battery container 45. Further, inside the battery container 45, a battery 81 is provided so as to be immersed in the working fluid. Therefore, the battery 81 can exchange heat with the working medium flowing through the battery container 45.

When cooling water having no insulating property is used as the working medium as described above, the cooling water is cooled in a water jacket provided in the battery container 45 in contact with the battery 81 so that the cooling water does not come into contact with the battery 81. It is preferable to let water flow. As a result, heat exchange can be performed between the battery 81 and the cooling water while ensuring the insulation between the battery 81 and the cooling water.

When the battery 81 needs to be cooled, the control device 7 drives the second pump 43 to obtain a predetermined flow rate in the order of the chiller 52, the heat exchanger 42, the second pump 43, and the battery container 45. Circulate the working medium with. The working medium circulating in the circulation flow path 41 is cooled by heat exchange with the organic medium circulating in the Rankine cycle circuit 5 in the chiller 52, cooled by heat exchange with the outside air in the heat exchanger 42, and the battery in the battery container 45. It is heated by heat exchange with 81. Therefore, the control device 7 can maintain the temperature of the battery 81 at a predetermined target temperature suitable for use by adjusting the flow rate of the working medium circulating in the circulation flow path 41 by using the second pump 43.

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, and a first pump 51 provided in the main circulation flow path 50. It includes a chiller 52, a heat exchanger 53, an evaporator 54, an expander 55, and a condenser 56.

The main circulation flow path 50 includes a first pump 51 that compresses an organic medium, a chiller 52 that exchanges heat between the working medium of the battery cooling circuit 4 and the organic medium, in the clockwise order in FIG. Between the heat exchanger 53 and the evaporator 54 that exchange heat between the cooling water of the engine cooling circuit 3 and the organic medium, the expander 55 that decompresses the organic medium that has passed through the evaporator 54, and the outside air and the organic medium. A condenser 56 for heat exchange is provided.

The first pump 51 is provided between the condenser 56 and the chiller 52 in the main circulation flow path 50. The first pump 51 is provided in the main circulation flow path 50 with the condenser 56 side as an inlet and the chiller 52 side as an outlet. The first pump 51 operates in response to a control signal from the control device 7, compresses the organic medium supplied from the condenser 56, and supplies the organic medium to the chiller 52. The rotation speed of the first pump 51 is adjusted by the control device 7.

The chiller 52 is provided between the first pump 51 and the heat exchanger 53 in the main circulation flow path 50. The chiller 52 is connected to the outlet of the first pump 51. The chiller 52 includes an organic medium flow path through which the organic medium flows and an operating medium flow path through which the working medium of the battery cooling circuit 4 passes, and heat exchanges between the organic medium and the working medium.

The heat exchanger 53 is provided between the chiller 52 and the evaporator 54 in the main circulation flow path 50. The heat exchanger 53 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 engine cooling circuit 3 passes, and heat exchanges between the organic medium and the cooling water.

The evaporator 54 is provided between the heat exchanger 53 and the expander 55 in the main circulation flow path 50. The evaporator 54 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 engine cooling circuit 3 passes, and heat exchanges between the organic medium and the cooling water.

The condenser 56 is connected to the inlet of the first pump 51. The condenser 56 includes an organic medium flow path through which the organic medium flows and a fan that supplies outside air to the organic medium flow path, and exchanges heat between the organic medium and the outside air.

The expander 55 is provided between the evaporator 54 and the condenser 56. The expander 55 decompresses the organic medium flowing from the evaporator 54 to the condenser 56. A motor generator 57 is connected to the drive shaft 55a of the expander 55. The motor generator 57 can transfer electric 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 expander 55, or generates electricity with the mechanical energy recovered in the process of depressurizing the organic medium in the expander 55, and the generated electric power is used to generate the battery 81. It is possible to charge the battery.

According to the thermal cycle system 1 as described above, by operating the first pump 51 of the Rankine cycle circuit 5 and the motor generator 57 by the control device 7, the battery 81 and its operating medium, the engine 2 and its cooling water are controlled. While cooling, a part of the waste heat of the battery 81 and the engine 2 can be recovered.

FIG. 2 is a diagram showing the flow of cooling water and the like realized in the engine cooling circuit 3, the battery cooling circuit 4, and the Rankine cycle circuit 5 when the hybrid cooling mode for cooling both the battery 81 and the engine 2 is executed. .. In the hybrid cooling mode, the control device 7 is an organic medium in the order of the first pump 51, the chiller 52, the heat exchanger 53, the evaporator 54, the expander 55, and the condenser 56, as shown by the thick arrows in FIG. Operate the Rankine cycle circuit 5 so that In the hybrid cooling mode, the control device 7 has a battery cooling circuit so that the working medium circulates in the order of the second pump 43, the battery container 45, the chiller 52, and the heat exchanger 42, as shown by the thick arrows in FIG. Operate 4. Further, in the hybrid cooling mode, the control device 7 is configured in the order of the first water pump 35, the first cooling water flow path 31, the bypass flow path 34, and the heat exchanger 53, as shown by the thick arrow in FIG. The engine cooling circuit 3 is operated so that the cooling water circulates along the first circulation flow path. Further, when the control device 7 recovers the heat of the exhaust of the engine 2 in the hybrid cooling mode, in addition to the first circulation flow path, the control device 7 has a first water pump 35, a first cooling water flow path 31, and a second water pump. The engine cooling circuit 3 is operated so that the cooling water circulates along the second circulation flow path composed of 36, the second cooling water flow path 32, the heater core 37, the evaporator 54, and the heat exchanger 53 in this order. In the hybrid cooling mode, the thermal cycle as shown in FIG. 3 is realized by operating the engine cooling circuit 3, the battery cooling circuit 4, and the Rankine cycle circuit 5 by the control device 7 as described above.

FIG. 3 is a Moriel diagram showing the thermal cycle realized in the Rankine cycle circuit 5 when the hybrid cooling mode is executed. As shown in FIG. 3, when the hybrid cooling mode is executed, the organic medium is compressed by the first pump 51 and supplied to the chiller 52 in the state of a supercooled liquid. The organic medium compressed by the first pump 51 is heated by heat exchange with the working medium circulating in the circulation flow path 41 of the battery cooling circuit 4 in the process of flowing through the chiller 52, and is supplied to the heat exchanger 53. The organic medium flowing out of the chiller 52 in the form of a supercooled liquid exchanges heat with the cooling water circulating in the first and second circulation channels of the engine cooling circuit 3 in the process of flowing through the heat exchanger 53 and the evaporator 54. It is heated by, which causes it to boil and become a superheated steam. The organic medium flowing out of the evaporator 54 in the state of superheated steam is depressurized in the expander 55 and supplied to the condenser 56 in the state of superheated steam. The organic medium supplied from the expander 55 is cooled by heat exchange with the outside air in the process of flowing through the condenser 56, and is supplied to the first pump 51 in the state of a supercooled liquid.

Here, in the hybrid cooling mode, the control device 7 is generated by the motor generator 57 by utilizing the mechanical energy generated in the drive shaft 55a in the process of depressurizing the organic medium in the expander 55, and the battery 81 is generated by the electric power obtained thereby. To charge. Therefore, when the hybrid cooling mode is executed, a part of the heat energy of the operating medium of the battery 81 and a part of the heat energy of the cooling water of the engine 2 are released to the outside air and recovered as electric energy by the motor generator 57. Therefore, this lowers the temperature of the battery 81, its operating medium, the engine 2, and its cooling water.

Here, in the hybrid cooling mode, the control device 7 maintains a state in which the organic medium flows out from the chiller 52 at a boiling point or a temperature slightly lower than the boiling point, and the organic medium is boiled in the heat exchanger 53 and the evaporator 54. In other words, the working medium of the battery 81 is cooled by the sensible heat of the organic medium in the chiller 52, and the cooling water of the engine 2 is cooled by the latent heat of the organic medium in the heat exchanger 53 and the evaporator 54. The first pump 51 and the motor generator 57 are operated so as to be performed.

By the way, the boiling point of the organic medium in the heat exchanger 53 and the evaporator 54 changes depending on the amount and pressure of the organic medium in the heat exchanger 53 and the evaporator 54. Therefore, in the hybrid cooling mode, the control device 7 flows out at a temperature at which the temperature of the organic medium flowing out from the chiller 52 is slightly lower than the boiling point or the boiling point, and the boiling point of the organic medium in the heat exchanger 53 and the evaporator 54 is the cooling water. The amount and pressure of the organic medium in the heat exchanger 53 and the evaporator 54 are controlled by using the first pump 51 and the motor generator 57 so as to be maintained at the target temperature of. More specifically, in the control device 7, the organic medium flows out from the chiller 52 at a boiling point or a temperature slightly lower than the boiling point, and the boiling point of the organic medium in the heat exchanger 53 and the evaporator 54 is maintained at the above target temperature. As described above, the target amount and target pressure of the organic medium in the heat exchanger 53 and the evaporator 54 are calculated, and the rotation speed of the first pump 51 and the power generation in the motor generator 57 are realized so that these target amounts and target pressures are realized. Adjust the amount.

According to the thermodynamic cycle system 1 of the present embodiment, the following effects are obtained.
(1) The thermal cycle system 1 includes an engine cooling circuit 3 in which cooling water that exchanges heat with the engine 2 and its exhaust is circulated, and a Rankine cycle circuit 5 in which an insulating organic medium circulates. Further, in the main circulation flow path 50 of the Rankine cycle circuit 5, an expander 55 for reducing the pressure of the organic medium in order along the flow of the organic medium, a condenser 56 for cooling the organic medium with outside air, an organic medium and a battery 81 are provided. A chiller 52 that exchanges heat with the working medium of the above, and a heat exchanger 53 and an evaporator 54 that exchange heat between the organic medium and the cooling water are provided. For example, in a hybrid vehicle equipped with both a battery 81 and an engine 2, the temperature range of the engine 2 is higher than that of the battery 81 in many situations. Therefore, in the heat cycle system 1, the chiller 52 that exchanges heat with the operating medium of the battery 81 whose temperature zone is lower than that of the engine 2 is condensed more than the heat exchanger 53 and the evaporator 54 that exchange heat with the cooling water of the engine 2. It is provided closer to the vessel 56. Therefore, according to the heat cycle system 1, the organic medium is circulated in the order of the expander 55, the condenser 56, the chiller 52, the heat exchanger 53, and the evaporator 54, so that the battery 81 having a lower temperature zone in the chiller 52 can be used. After cooling the working medium, the cooling water of the engine 2 having a higher temperature range can be further cooled by the organic medium heated by the heat exchange in the chiller 52. Therefore, according to the thermal cycle system 1, both the battery 81 and the engine 2 having different temperature zones can be efficiently cooled by the organic medium circulating in the Rankine cycle circuit 5.

(2) In the heat cycle system 1, in the control device 7, the operating medium of the battery 81 is cooled by the sensible heat of the organic medium in the chiller 52, and the cooling water of the engine 2 is the organic medium in the heat exchanger 53 and the evaporator 54. The first pump 51 is operated so as to be cooled by latent heat. Here, when cooling by the latent heat of the organic medium, the temperature of the organic medium can be kept constant at a predetermined target temperature, so that the cooling can be performed more efficiently than the case of cooling by sensible heat. Therefore, according to the thermodynamic cycle system 1, both the battery 81 and the engine 2 having a higher temperature range can be efficiently cooled by the organic medium circulating in the circulation flow path.

(3) The thermal cycle system 1 includes a battery cooling circuit 4 in which a working medium that exchanges heat with the battery 81 circulates. Further, in the thermal cycle system 1, the working medium circulating in the battery cooling circuit 4 is heat exchangeable with the organic medium in the chiller 52. Thereby, for example, by stopping the circulation of the working medium in the battery cooling circuit 4 while circulating the organic medium in the Rankine cycle circuit 5, only the engine 2 can be positively cooled.

(4) The thermodynamic cycle system 1 further includes a motor generator 57 connected to the expander 55. As a result, the motor generator 57 functions as a generator while circulating the organic medium in the order of the expander 55, the condenser 56, the chiller 52, the heat exchanger 53, and the evaporator 54, whereby the chiller 52, the heat exchanger 53, In the process of reducing the pressure of the organic medium heated by the heat exchange in the evaporator 54 in the expander 55, a part of the waste heat of the battery 81 and the engine 2 can be recovered as electric energy. Further, according to the heat cycle system 1, effective heat exchange is performed between the organic medium and the working medium of the battery 81 and the cooling water of the engine 2 in the chiller 52, the heat exchanger 53 and the evaporator 54. The motor generator 57 can also be used to control the pressure of the organic medium in the chiller 52, heat exchanger 53 and evaporator 54.

<Second Embodiment>
Hereinafter, the second embodiment of the present invention will be described with reference to the drawings.
FIG. 4 is a diagram showing the configuration of the thermal cycle system 1A according to the present embodiment. The thermodynamic cycle system 1A has a different configuration of the Rankine cycle circuit 5A from the thermodynamic cycle system 1 according to the first embodiment. In the following description of the thermal cycle system 1A, the same components as those of the thermal cycle system 1 are designated by the same reference numerals, and detailed description thereof will be omitted.

The Rankine cycle circuit 5A includes a main circulation flow path 50A in which an insulating organic medium having a boiling point and a lower specific heat than cooling water circulates, a first pump 51A provided in the main circulation flow path 50A, and an electronic expansion valve. 58, a battery container 65, a heat exchanger 53, an evaporator 54, a compression expander 59, and a condenser 56, and a bypass flow path 60 that bypasses a part of a plurality of devices provided in the main circulation flow path 50A. A second pump 64 provided in the bypass flow path 60 is provided.

The compression expander 59 is provided between the evaporator 54 and the condenser 56 in the main circulation flow path 50A. The compression expander 59 decompresses the organic medium flowing through the main circulation flow path 50A from the evaporator 54 side to the condenser 56 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 50A from the condenser 56 side to the evaporator 54 side is compressed (hereinafter, this flow direction is also referred to as "second flow direction F2"). The compression expander 59 decompresses the organic medium that has passed through the evaporator 54 and supplies it to the condenser 56 at the time of normal rotation in which the organic medium flows through the main circulation flow path 50A along the first flow direction F1. Further, the compression expander 59 compresses the organic medium that has passed through the condenser 56 and supplies it to the evaporator 54 at the time of reversal in which the organic medium flows through the main circulation flow path 50A along the second flow direction F2.

A motor generator 57 is connected to the drive shaft 59a of the compression expander 59. The motor generator 57 can transfer electric energy to and from the battery 81 in response to a control signal from the control device 7A. Therefore, the motor generator 57 uses the electric power supplied from the battery 81 to rotate the compression / expander 59 in the forward or reverse direction, or generates electricity with the mechanical energy recovered in the process of depressurizing the organic medium in the compression / expansion machine 59. It is possible to charge the battery 81 with the generated power.

The condenser 56 is provided on the downstream side of the compression expander 59 along the first flow direction F1 in the main circulation flow path 50A. The evaporator 54 is provided on the upstream side of the compression expander 59 along the first flow direction F1 in the main circulation flow path 50A. The heat exchanger 53 is provided on the upstream side of the evaporator 54 along the first flow direction F1 in the main circulation flow path 50A.

The battery container 65 is provided on the upstream side of the heat exchanger 53 along the first flow direction F1 in the main circulation flow path 50A. An organic medium passes through the inside of the battery container 65. Further, inside the battery container 65, 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 65.

The portion of the main circulation flow path 50A between the condenser 56 and the battery container 65 is branched into a first branch path 501 and a second branch path 502. Further, a first pump 51A is provided in the first branch passage 501, and an electronic expansion valve 58 is provided in the second branch passage 502. That is, the first pump 51A and the electronic expansion valve 58 are provided in parallel in the main circulation flow path 50A.

The first pump 51A is provided on the downstream side of the condenser 56 and the upstream side of the battery container 65 along the first flow direction F1 in the first branch path 501. The first pump 51A operates in response to a control signal from the control device 7A to compress an organic medium flowing along the first flow direction F1 in the first branch path 501. The rotation speed of the first pump 51A is adjusted by the control device 7A.

The electronic expansion valve 58 is provided on the downstream side of the battery container 65 and on the upstream side of the condenser 56 along the second flow direction F2 in the second branch path 502. The electronic expansion valve 58 is a throttle valve and reduces the pressure of the organic medium flowing along the second flow direction F2 in the second branch path 502. The opening degree of the electronic expansion valve 58 is adjusted according to the control signal from the control device 7A.

From the above, in the order along the first flow direction F1, the main circulation flow path 50A includes a compression expander 59, a condenser 56, a first pump 51A, a battery container 65, and a heat exchanger 53. , And an evaporator 54 are provided. Further, in the order along the second flow direction F2, the compression expander 59, the evaporator 54, the heat exchanger 53, the battery container 65, the electronic expansion valve 58, and the condensation are condensed in the main circulation flow path 50A. A vessel 56 is provided.

The bypass flow path 60 connects between the condenser 56 and the branch paths 501 and 502 of the main circulation flow path 50A and between the battery container 65 and the heat exchanger 53. That is, the bypass flow path 60 forms a flow path that bypasses the first pump 51A, the electronic expansion valve 58, and the battery container 65 in the main circulation flow path 50A.

The second pump 64 operates in response to a control signal from the control device 7A to compress the organic medium flowing along the first flow direction F1 in the main circulation flow path 50A. The rotation speed of the second pump 64 is adjusted by the control device 7A. That is, by turning on the second pump 64, a part of the organic medium flowing out from the condenser 56 along the first flow direction F1 is detoured from the first pump 51A, the electronic expansion valve 58, and the battery container 65. Then, it is returned to the heat exchanger 53.

According to the thermal cycle system 1A as described above, various controls are performed by operating the first pump 51A, the motor generator 57, the electronic expansion valve 58, the second pump 64, etc. of the Rankine cycle circuit 5A by the control device 7A. The Rankine cycle circuit 5A can be operated in the mode.

FIG. 5 is a diagram showing the flow of cooling water and the like realized in the engine cooling circuit 3 and the Rankine cycle circuit 5A when the hybrid cooling mode for cooling both the battery 81 and the engine 2 is executed. In the hybrid cooling mode, the control device 7A has the first pump 51A, the battery container 65, the heat exchanger 53, the evaporator 54, the compression expander 59, and the condenser 56 in this order, as shown by the thick arrow in FIG. Two circulations, a first circulation flow path configured and a second circulation flow path configured in the order of a second pump 64, a heat exchanger 53, an evaporator 54, a compression expander 59, and a condenser 56. The Rankine cycle circuit 5A is operated so that the organic medium circulates along the flow path. Further, in the hybrid cooling mode, the control device 7A is configured in the order of the first water pump 35, the first cooling water flow path 31, the bypass flow path 34, and the heat exchanger 53, as shown by the thick arrow in FIG. The engine cooling circuit 3 is operated so that the cooling water circulates along the third circulation flow path. Further, when the control device 7A recovers the heat of the exhaust of the engine 2 in the hybrid cooling mode, in addition to the third circulation flow path, the first water pump 35, the first cooling water flow path 31, and the second water pump The engine cooling circuit 3 is operated so that the cooling water circulates along the fourth circulation flow path composed of 36, the second cooling water flow path 32, the heater core 37, the evaporator 54, and the heat exchanger 53 in this order. In the hybrid cooling mode, the thermal cycle as shown in FIG. 6 is realized by operating the engine cooling circuit 3 and the Rankine cycle circuit 5A by the control device 7A as described above.

FIG. 6 is a Moriel diagram showing the thermal cycle realized in the Rankine cycle circuit 5A when the hybrid cooling mode is executed. As shown in FIG. 6, when the hybrid cooling mode is executed, the organic medium is compressed by the first pump 51A and supplied to the battery container 65 in the state of a supercooled liquid. The organic medium compressed by the first pump 51A is heated by heat exchange with the battery 81 in the process of flowing through the battery container 65, and is supplied to the heat exchanger 53 in a liquid state. The organic medium flowing out of the battery container 65 in a liquid state is further heated by heat exchange with cooling water in the process of flowing through the heat exchanger 53 and the evaporator 54, and is further heated to the compression expander 59 in a superheated steam or boiling state. Will be supplied. The organic medium flowing out of the evaporator 54 in the state of superheated steam is depressurized in the compression expander 59 and supplied to the condenser 56 in the state of superheated steam. The organic medium supplied from the compression expander 59 is cooled by heat exchange with the outside air in the process of flowing through the condenser 56, and is supplied to the first pump 51A in the state of a supercooled liquid. Further, as described above, in the hybrid cooling mode, the second pump 64 is turned on in addition to the first pump 51A. Therefore, a part of the organic medium flowing out of the condenser 56 in the state of the supercooled liquid is compressed by the second pump 64 and supplied to the heat exchanger 53 and the evaporator 54 in the state of the supercooled liquid.

Here, in the hybrid cooling mode, the control device 7A is generated by the motor generator 57 by utilizing the mechanical energy generated in the drive shaft 59a in the process of depressurizing the organic medium in the compression expander 59, and the battery is generated by the electric power obtained thereby. Charge 81. Therefore, when the 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 of the engine 2 are released to the outside air and recovered as electric energy by the motor generator 57. As a result, the temperatures of the battery 81, the cooling water, and the engine 2 are lowered.

Here, in the hybrid cooling mode, the control device 7A is maintained in a state where the organic medium flows out from the battery container 65 at a temperature slightly lower than the boiling point and the organic medium is boiled in the heat exchanger 53 and the evaporator 54. In other words, the battery 81 is cooled by the sensible heat of the organic medium in the battery container 65, and the cooling water is cooled by the latent heat of the organic medium in the heat exchanger 53 and the evaporator 54. The first pump 51A, the second pump 64, and the motor generator 57 are operated.

Further, in the control device 7A, in the hybrid cooling mode, the temperature of the organic medium flowing out from the battery container 65 flows out at a temperature slightly lower than the boiling point, and the boiling point of the organic medium in the heat exchanger 53 and the evaporator 54 is the cooling water. A first pump 51A, a second pump 64, and a motor generator 57 are used to control the amount and pressure of the organic medium in the heat exchanger 53 and the evaporator 54 so that the target temperature is maintained. More specifically, in the control device 7A, the organic medium flows out from the battery container 65 at a temperature slightly lower than the boiling point, and the boiling point of the organic medium in the heat exchanger 53 and the evaporator 54 is maintained at the above target temperature. As described above, the target amount of the organic medium in the battery container 65 and the target amount and the target pressure of the organic medium in the heat exchanger 53 and the evaporator 54 are calculated, and the amount of the organic medium in the battery container 65 becomes the above target amount. The rotation speed of the first pump 51A is adjusted, the rotation speed of the second pump 64 is adjusted so that the amount of the organic medium in the heat exchanger 53 and the evaporator 54 becomes the above target amount, and the heat exchanger 53 and the heat exchanger 53 and The amount of heat generated by the motor generator 57 is adjusted so that the pressure of the organic medium in the evaporator 54 becomes the target pressure.

According to the thermodynamic cycle system 1A of the present embodiment, the following effects are obtained.
(5) The thermal cycle system 1A includes an engine cooling circuit 3 in which cooling water that exchanges heat with the internal combustion engine and its exhaust is circulated, and a Rankine cycle circuit 5A in which an insulating organic medium circulates. Further, in the main circulation flow path 50A of the Rankine cycle circuit 5A, a compression expander 59 for reducing the pressure of the organic medium in order along the flow of the organic medium, a condenser 56 for cooling the organic medium with the outside air, an organic medium and a battery are provided. A battery container 65 that exchanges heat with the 81, and a heat exchanger 53 and an evaporator 54 that exchange heat between the organic medium and the cooling water of the engine 2 are provided. Further, in the heat cycle system 1A, the battery container 65 that exchanges heat with the battery 81 whose temperature zone is lower than that of the engine 2 is the condenser 56 rather than the heat exchanger 53 and the evaporator 54 that exchange heat with the cooling water of the engine 2. Install closer to. Therefore, according to the heat cycle system 1A, the temperature zone of the battery container 65 is lower by circulating the organic medium in the order of the compression expander 59, the condenser 56, the battery container 65, the heat exchanger 53, and the evaporator 54. After cooling the battery 81, the cooling water of the engine 2 having a higher temperature range can be further cooled by the organic medium heated by the heat exchange in the battery container 65. Therefore, according to the present invention, the organic medium circulating in the Rankine cycle circuit 5A can efficiently cool both the engine 2 and the engine 2 having different temperature zones.

Although one embodiment of the present invention has been described above, the present invention is not limited to this. Within the scope of the present invention, the detailed configuration may be changed as appropriate.

1,1A ... Thermal cycle system 2 ... Engine (internal combustion engine)
3 ... Engine cooling circuit (internal combustion engine cooling circuit)
4 ... Battery cooling circuit (electrical device cooling circuit)
5,5A ... Rankine cycle circuit 50, 50A ... Main circulation flow path (circulation flow path)
51, 51A ... 1st pump (pump)
52 ... Chiller (1st heat exchange section)
53 ... Heat exchanger (second heat exchanger)
54 ... Evaporator (second heat exchanger)
55 ... Inflator 56 ... Condenser 59 ... Compression inflator (expansion)
57 ... Motor generator 65 ... Battery container (1st heat exchange section)
7,7A ... Control device 81 ... Battery (electrical device)

Claims (4)

An internal combustion engine cooling circuit in which cooling water that exchanges heat with the internal combustion engine and its exhaust circulates, and a Rankine cycle circuit in which an insulating organic medium circulates.
A thermodynamic cycle system including a control device for operating the Rankine cycle circuit .
In the circulation flow path of the Rankine cycle circuit, in order along the flow of the organic medium,
An expander that decompresses the organic medium,
A condenser that cools the organic medium with the outside air,
The first pump that compresses the organic medium and
A first heat exchange unit that exchanges heat between an organic medium and an electric device or an operating medium capable of exchanging heat between the electric device and the electric device.
A second heat exchange unit that exchanges heat between the organic medium and the cooling water is provided .
The control device is such that the electric device or the operating medium is cooled by the sensible heat of the organic medium in the first heat exchange section and the cooling water is cooled by the latent heat of the organic medium in the second heat exchange section. 1 A thermal cycle system characterized by operating a pump . The Rankine cycle circuit includes a bypass flow path connecting the condenser and the first pump and the first heat exchange section and the second heat exchange section of the circulation flow path, and the bypass flow. The heat cycle system according to claim 1 , further comprising a second pump provided on the road . An electric device cooling circuit for circulating an operating medium that exchanges heat with the electric device is provided.
The heat cycle system according to claim 1 or 2, wherein the working medium circulating in the electric device cooling circuit can exchange heat with an organic medium in the first heat exchange unit. The thermodynamic cycle system according to any one of claims 1 to 3, further comprising a motor generator connected to the expander.

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