Heat Exchange System

Abstract

To provide a heat exchange system capable of securing an adjustment width of distribution to heat absorbing capacity for absorbing heat from blown air to be blown to an air-conditioning object space and heat absorbing capacity for absorbing heat from a heat absorption medium.SOLUTION: A heat exchange system 1 includes: a compressor 11; a condenser 12; a first pressure reduction valve 14; an evaporator for air conditioning 15; a second pressure reduction valve 17 disposed in parallel with the first pressure reduction valve 14 at a downstream side of the condenser 12; and an evaporator 18 for a first apparatus to absorb heat from a heat generation apparatus 63 and the like through a low temperature-side heat medium. The heat exchange system 1 includes an evaporator 20 for a second apparatus to adjust a heat absorption amount from the low temperature-side heat medium by heat exchange of a refrigerant with the low temperature-side heat medium. The heat exchange system 1 is constituted to adjust distribution of heat absorbing capacity for absorbing heat from blown air and heat absorbing capacity for absorbing heat from the low temperature-side heat medium by changing a heat exchange amount in one of heat exchangers of the evaporator 18 for the first apparatus and the evaporator 20 for the second apparatus.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present disclosure relates to a heat exchange system. [Background technology]

[0002] Conventionally, there is known an air conditioner that has an evaporator that exchanges heat between a refrigerant and a heat medium in addition to an evaporator that exchanges heat between the air and the refrigerant, and that can realize heating and cooling of equipment such as heat-generating bodies by transferring heat from a low-temperature side to a high-temperature side using a compressor (see, for example, Patent Document 1). Each evaporator constitutes a heat absorber that absorbs heat from the air or the heat medium. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 6791052 Summary of the Invention [Problem to be solved by the invention]

[0004] The inventors are considering a heat exchange system having two heat absorbers, namely, an evaporator that absorbs heat from the blown air blown into the space to be air-conditioned, and an evaporator that absorbs heat from a heat absorbing medium that absorbs heat from a heat generating device or an external space. In the heat exchange system under consideration, it is important to ensure an adjustment range for the distribution of the heat absorption capacity that absorbs heat from the blown air and the heat absorption capacity that absorbs heat from the heat absorption medium in order to respond to various scenes, but this is not considered at all in Patent Document 1, and there is room for improvement.

[0005] The present disclosure aims to provide a heat exchange system that can ensure an adjustable range for the distribution between the heat absorption capacity for absorbing heat from the air blown into a space to be air-conditioned and the heat absorption capacity for absorbing heat from a heat absorption medium. [Means for solving the problem]

[0006] The invention described in claim 1 is 1. A heat exchange system comprising: a compressor (11) that compresses and discharges a refrigerant; a radiator (12) that radiates heat by exchanging heat between a refrigerant discharged from the compressor and a heat radiating medium that radiates heat to at least one of an external space and a space to be air-conditioned; a first pressure reducing section (14) that reduces the pressure of the refrigerant that has passed through the radiator; a second pressure reducing section (17) that is disposed in parallel with the first pressure reducing section downstream of the radiator and reduces the pressure of the refrigerant that has passed through the radiator; a first evaporator (15) that evaporates the refrigerant decompressed in the first decompression section by exchanging heat with air to be blown into the space to be air-conditioned; a second evaporator (18) that evaporates the refrigerant decompressed in the second decompression section by heat exchange with a heat absorbing medium that absorbs heat from at least one of the heat generating device (63) and an external space; a heat absorbing heat exchanger (20, 20A, 21) for adjusting the amount of heat absorbed from a heat absorbing medium by exchanging heat between a refrigerant and a predetermined fluid; The heat exchanger includes a capacity adjusting section (100a) that adjusts the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium by changing the heat exchange amount in one of the second evaporator and the heat absorption heat exchanger.

[0007] According to this, the amount of heat absorbed from the heat absorbing medium is adjusted by two heat absorbers, namely, the second evaporator and the heat exchanger for absorbing heat, so that the adjustment range of the heat absorbing capacity of the heat absorbing medium can be increased. And, the heat absorbing capacity of the heat absorbing medium changes according to the heat absorbing capacity of the heat absorbing medium.

[0008] Therefore, according to the heat exchange system of the present disclosure, it is possible to ensure an adjustment range for the distribution between the heat absorption capacity of the heat absorption medium and the heat absorption capacity of the air blown into the air-conditioned space. In particular, the wide adjustment range of the heat absorption capacity of the heat absorption medium has the advantage that it is easier to appropriately adjust the temperature of heat-generating devices that generate a large amount of heat, such as batteries.

[0009] The reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and specific components described in the embodiments described below. [Brief description of the drawings]

[0010] [Figure 1] 1 is a schematic configuration diagram of a heat exchange system according to a first embodiment. [Diagram 2] FIG. 2 is an explanatory diagram for explaining a cycle configuration of a refrigeration cycle of the heat exchange system according to the first embodiment. [Diagram 3] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through the refrigeration cycle when the opening area of ​​the second pressure reducing valve is enlarged. [Figure 4] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through the refrigeration cycle when the opening area of ​​the first pressure reducing valve is enlarged. [Diagram 5] 4 is an explanatory diagram for explaining the state of the refrigerant in the air conditioning evaporator when the opening area of ​​the first pressure reducing valve is enlarged. FIG. [Figure 6] 10A and 10B are explanatory diagrams for explaining the states of the pressure reducing valves in an air conditioning priority scene and a heat absorption priority scene. [Figure 7] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through a refrigeration cycle when an air conditioning priority scene occurs. [Figure 8] FIG. 4 is an explanatory diagram for explaining the state of refrigerant in the first device evaporator and the second device evaporator when an air conditioning priority scene occurs. [Figure 9] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through a refrigeration cycle when an equipment priority scene is entered. [Figure 10] FIG. 4 is an explanatory diagram for explaining the state of refrigerant in a first device evaporator and a second device evaporator when a device priority scene occurs. [Figure 11] FIG. 2 is an explanatory diagram for explaining a cycle configuration of a refrigeration cycle of a heat exchange system which is a first modified example of the first embodiment. [Figure 12] FIG. 11 is an explanatory diagram for explaining a cycle configuration of a refrigeration cycle of a heat exchange system according to a second modified example of the first embodiment. [Figure 13] FIG. 13 is an explanatory diagram for explaining a cycle configuration of a refrigeration cycle of a heat exchange system according to a third modified example of the first embodiment. [Figure 14] FIG. 11 is an explanatory diagram for explaining the cycle configuration of a refrigeration cycle of a heat exchange system according to a second embodiment. [Figure 15] 10A and 10B are explanatory diagrams for explaining the states of the pressure reducing valves in an air conditioning priority scene and a heat absorption priority scene. [Figure 16] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through a refrigeration cycle when an air conditioning priority scene occurs. [Figure 17] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through a refrigeration cycle when an equipment priority scene is entered. [Figure 18] 13 is an explanatory diagram for explaining the state of each pressure reducing valve in an air conditioning priority scene and a heat absorption priority scene in a heat exchange system that is a first modified example of the second embodiment. FIG. [Figure 19] FIG. 13 is an explanatory diagram for explaining a cycle configuration of a refrigeration cycle of a heat exchange system that is a second modified example of the second embodiment. [Figure 20] FIG. 11 is an explanatory diagram for explaining the cycle configuration of a refrigeration cycle of a heat exchange system according to a third embodiment. [Figure 21] 10A and 10B are explanatory diagrams for explaining the states of the pressure reducing valves in an air conditioning priority scene and a heat absorption priority scene. [Figure 22] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through a refrigeration cycle when an air conditioning priority scene occurs. [Diagram 23] FIG. 13 is an explanatory diagram for explaining the cycle configuration of a refrigeration cycle of a heat exchange system according to a fourth embodiment. [Figure 24] FIG. 4 is a Mollier diagram showing the state of a refrigerant flowing through a refrigeration cycle when an air conditioning priority scene occurs. [Diagram 25] 10A and 10B are explanatory diagrams for explaining the states of the pressure reducing valves in an air conditioning priority scene and a heat absorption priority scene. [Figure 26]FIG. 13 is an explanatory diagram for explaining a first device evaporator and a second device evaporator employed in a heat exchange system according to a fifth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0011] Hereinafter, the embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same reference numerals are used for parts that are the same as or equivalent to those described in the preceding embodiments, and the description thereof may be omitted. In addition, in the embodiments, when only a part of the components is described, the components described in the preceding embodiments can be applied to the other parts of the components. In the following embodiments, each embodiment can be partially combined with each other, even if not specifically stated, as long as it does not cause any trouble in combination.

[0012] (First embodiment) This embodiment will be described with reference to Figs. 1 to 10. In this embodiment, an example will be described in which a heat exchange system 1 of the present disclosure is applied to an air conditioning system for a vehicle. The heat exchange system 1 is mounted, for example, on an electric vehicle that obtains driving force for running the vehicle from a running electric motor. The electric vehicle is capable of charging a large-capacity battery BT mounted on the vehicle with power supplied from an external power source when the vehicle is stopped. The battery BT is a secondary battery that can be charged and discharged. The battery BT is, for example, a lithium-ion battery that has a high energy density and is lightweight and compact.

[0013] 1, the heat exchange system 1 includes a vapor compression refrigeration cycle 10, a high-temperature side circuit 50, a low-temperature side circuit 60, and a control unit 100. The heat exchange system 1 conditions the interior of a vehicle as a space to be air-conditioned, and adjusts the temperature of heat-generating devices 63 including a battery BT.

[0014] The refrigeration cycle 10 has a compressor 11, a condenser 12, a liquid receiving section 13, a first pressure reducing valve 14, an air conditioning evaporator 15, an evaporation pressure control valve 16, a second pressure reducing valve 17, an evaporator 18 for the first equipment, a third pressure reducing valve 19, and an evaporator 20 for the second equipment.

[0015] The refrigeration cycle 10 employs a refrigerant with a low global warming potential, such as HFO-1234yf. The refrigerant contains a refrigeration oil for lubricating the compressor 11. The refrigeration oil employed is, for example, a refrigeration oil compatible with a liquid phase refrigerant, such as PAG oil. A portion of the refrigeration oil circulates within the refrigeration cycle 10 together with the refrigerant.

[0016] The compressor 11 is a device that compresses and discharges a refrigerant. The compressor 11 is configured as an electric compressor that is driven by power supplied from the battery BT. The operation of the compressor 11 is controlled by a control signal output from the control unit 100.

[0017] A condenser 12 is connected to the refrigerant discharge side of the compressor 11. The condenser 12 is a heat radiator that exchanges heat between a high-temperature, high-pressure refrigerant (hereinafter also referred to as high-pressure refrigerant) discharged from the compressor 11 and a high-temperature side heat medium flowing through a high-temperature side circuit 50, and radiates heat from the high-pressure refrigerant to the high-temperature side heat medium. When passing through the condenser 12, the high-pressure refrigerant radiates heat to the high-temperature side heat medium and is condensed. In this embodiment, the high-temperature side heat medium corresponds to the "heat radiating medium".

[0018] The high-temperature side heat medium is a fluid that flows through the high-temperature side circuit 50. The high-temperature side heat medium is a liquid-phase fluid that does not change phase when flowing through the high-temperature side circuit 50. For example, a liquid containing ethylene glycol or an antifreeze liquid is used as the high-temperature side heat medium.

[0019] The high-temperature side circuit 50 is a circuit for dissipating heat from the high-temperature side heat medium to the outside and for heating the vehicle interior using the high-temperature side heat medium. The high-temperature side circuit 50 is provided with a high-temperature side pump 51, a high-temperature side radiator 52, an electric heater 53, a heater core 54, a first flow path switching valve 55, and a high-temperature side reserve tank 56.

[0020] The high-temperature side pump 51 sucks in the high-temperature side heat medium and sends it out toward the condenser 12 side, thereby circulating the high-temperature side heat medium within the high-temperature side circuit 50. The high-temperature side pump 51 is an electric pump that is driven by power supplied from the battery BT. The high-temperature side pump 51 also functions as an adjustment means for adjusting the flow rate of the high-temperature side heat medium flowing through the high-temperature side circuit 50.

[0021] High-temperature side radiator 52 dissipates heat from the high-temperature side heat medium by exchanging heat between the high-temperature side heat medium heated in condenser 12 and the outside air outside the vehicle cabin. High-temperature side radiator 52 is disposed, for example, on the front side in the traveling direction of the vehicle, and traveling wind flows into it when the vehicle is traveling.

[0022] The electric heater 53 is arranged in parallel with the high-temperature side radiator 52 in the high-temperature side circuit 50. The electric heater 53 heats the high-temperature side heat medium. The electric heater 53 is an auxiliary heat source that heats the high-temperature side heat medium in a situation where the high-temperature side heat medium cannot be sufficiently heated by the condenser 12. The energized state of the electric heater 53 is controlled by a control signal output from the control unit 100.

[0023] The heater core 54 is disposed in series with the electric heater 53. The heater core 54 is disposed inside the casing 41 of the air conditioning unit 40. The heater core 54 generates conditioned air at a desired temperature by exchanging heat between the high-temperature side heat medium heated in the condenser 12 and the blown air to be blown into the vehicle cabin.

[0024] The first flow path switching valve 55 functions as a flow path switching unit that switches the flow path of the high-temperature side heat medium. The first flow path switching valve 55 is provided at a branching unit that branches the flow path of the high-temperature side heat medium in the high-temperature side circuit 50 into a flow path on the high-temperature side radiator 52 side and a flow path on the heater core 54 side. The first flow path switching valve 55 is configured as an electromagnetic three-way valve, and its operation is controlled by a control signal output from the control unit 100.

[0025] The high-temperature side reserve tank 56 is a tank for storing surplus high-temperature side heat medium. The high-temperature side reserve tank 56 is disposed on the inlet side of the high-temperature side heat medium in the high-temperature side pump 51.

[0026] A liquid receiving section 13 is connected to the refrigerant outlet side of the condenser 12. The liquid receiving section 13 stores surplus refrigerant in the refrigeration cycle 10. The liquid receiving section 13 separates the refrigerant flowing out from the condenser 12 into gas and liquid phases, and causes the separated liquid phase refrigerant to flow downstream. The liquid receiving section 13 may be configured as either a receiver tank with a refrigerant inlet and outlet provided at the top, or a modulator tank with a refrigerant inlet and outlet provided at the bottom. A first pressure reducing valve 14, a second pressure reducing valve 17, and a third pressure reducing valve 19 are connected to the refrigerant outlet side of the liquid receiving section 13 in parallel with each other.

[0027] The first pressure reducing valve 14 is a first pressure reducing section that reduces the pressure of the refrigerant that has passed through the condenser 12. Specifically, the first pressure reducing valve 14 reduces the pressure of the liquid phase refrigerant that has passed through the condenser 12 and accumulated in the liquid receiving section 13. The first pressure reducing valve 14 is an electrically variable throttle whose operation is controlled by a control signal output from the control section 100, and includes a valve body and an electric actuator. The first pressure reducing valve 14 is configured as a variable throttle with a full closing function that can substantially stop the flow of the refrigerant.

[0028] An air conditioning evaporator 15 is connected to the refrigerant outlet side of the first pressure reducing valve 14. The air conditioning evaporator 15 is disposed inside the casing 41 of the air conditioning unit 40 together with the heater core 54. The air conditioning evaporator 15 evaporates the refrigerant decompressed by the first pressure reducing valve 14 by heat exchange with the air to be blown into the vehicle cabin. In the air conditioning evaporator 15, the refrigerant absorbs heat from the air to be blown into the vehicle cabin and evaporates, thereby cooling the air. The air that has passed through the air conditioning evaporator 15 passes through the heater core 54 and is then supplied to the vehicle cabin as conditioned air. In this embodiment, the air conditioning evaporator 15 corresponds to the "first evaporator."

[0029] An evaporation pressure regulating valve 16 is connected to the refrigerant outlet side of the air conditioning evaporator 15. The evaporation pressure regulating valve 16 is a pressure adjusting unit that maintains the evaporation pressure of the refrigerant in the air conditioning evaporator 15 at a predetermined reference pressure or higher. The evaporation pressure regulating valve 16 is configured to adjust the evaporation pressure of the refrigerant in the air conditioning evaporator 15 so that the temperature of the air conditioning evaporator 15 becomes a temperature (e.g., 1°C) at which frost formation on the air conditioning evaporator 15 is suppressed. The evaporation pressure regulating valve 16 may be configured to drive a valve body by a mechanical drive mechanism using a bellows or the like, or may be configured to drive a valve body by an electric motor.

[0030] The second pressure reducing valve 17 is disposed in parallel with the first pressure reducing valve 14 downstream of the condenser 12. The second pressure reducing valve 17 is a second pressure reducing section that reduces the pressure of the refrigerant that has passed through the condenser 12. Specifically, the second pressure reducing valve 17 reduces the pressure of the liquid phase refrigerant that has passed through the condenser 12 and been stored in the liquid receiving section 13. The second pressure reducing valve 17 is an electrically variable throttle whose operation is controlled by a control signal output from the control section 100, and includes a valve body and an electric actuator. The second pressure reducing valve 17 is configured as a variable throttle with a full closing function that can substantially stop the flow of the refrigerant. The operation of the second pressure reducing valve 17 will be described later.

[0031] The refrigerant outlet side of the second pressure reducing valve 17 is connected to the first equipment evaporator 18. The first equipment evaporator 18 is a chiller that evaporates the refrigerant decompressed by the second pressure reducing valve 17 by heat exchange with a low-temperature side heat medium that absorbs heat from at least one of the heat generating device 63 or the outside air outside the vehicle cabin, which is the external space. In this embodiment, the outside of the vehicle cabin corresponds to the "external space", and the low-temperature side heat medium corresponds to the "heat absorbing medium" that absorbs heat from at least one of the heat generating device 63 or the external space. Also, in this embodiment, the first equipment evaporator 18 corresponds to the "second evaporator".

[0032] The third pressure reducing valve 19 is disposed in parallel with the first pressure reducing valve 14 and the second pressure reducing valve 17 on the downstream side of the condenser 12. The third pressure reducing valve 19 is a third pressure reducing section that reduces the pressure of the refrigerant that has passed through the condenser 12. Specifically, the third pressure reducing valve 19 reduces the pressure of the liquid phase refrigerant that has passed through the condenser 12 and been stored in the liquid receiving section 13. The third pressure reducing valve 19 is an electric variable throttle whose operation is controlled by a control signal output from the control section 100, and includes a valve body and an electric actuator. The third pressure reducing valve 19 is configured as a variable throttle with a full closing function that can substantially stop the flow of the refrigerant. The operation of the third pressure reducing valve 19 will be described later.

[0033] A second equipment evaporator 20 is connected to the refrigerant outlet side of the third pressure reducing valve 19. The second equipment evaporator 20 is a chiller that evaporates the refrigerant depressurized by the third pressure reducing valve 19 by heat exchange with a low-temperature heat medium that absorbs heat from at least one of the heat generating equipment 63 and the outside air outside the vehicle cabin, which is the external space. In this embodiment, the equipment evaporator 20 corresponds to the "heat absorbing heat exchanger" and the "third evaporator".

[0034] A refrigerant junction is provided on the refrigerant outlet side of the second equipment evaporator 20. This refrigerant junction is a three-way valve that joins the refrigerant that has passed through the air conditioning evaporator 15, the refrigerant that has passed through the first equipment evaporator 18, and the refrigerant that has passed through the second equipment evaporator 20. The refrigerant outlet side of the refrigerant junction is connected to the refrigerant suction port of the compressor 11.

[0035] Here, the low-temperature side heat medium is a fluid that flows through the low-temperature side circuit 60. The low-temperature side heat medium is a liquid-phase fluid that does not change phase when flowing through the low-temperature side circuit 60. For example, a liquid containing ethylene glycol or an antifreeze liquid is used as the low-temperature side heat medium. An oil having electrical insulation properties may also be used as the low-temperature side heat medium.

[0036] The low-temperature side circuit 60 is a heat absorption circuit through which a low-temperature side heat medium flows as a heat absorption medium. The low-temperature side circuit 60 is a circuit for adjusting the temperature of a heat generating device 63 using the low-temperature side heat medium and absorbing heat from an external space using the low-temperature side heat medium. In addition to the first device evaporator 18 and the second device evaporator 20, the low-temperature side circuit 60 is provided with a low-temperature side pump 61, a low-temperature side radiator 62, a heat generating device 63 to be temperature-adjusted, a second flow path switching valve 64, a low-temperature side reserve tank 65, and a third flow path switching valve 66.

[0037] The low-temperature side pump 61 sucks in the low-temperature side heat medium and sends it out toward the equipment evaporators 18, 20, thereby circulating the low-temperature side heat medium within the low-temperature side circuit 60. The low-temperature side pump 61 is an electric pump that is driven by power supplied from the battery BT. The low-temperature side pump 61 also functions as an adjustment means for adjusting the flow rate of the low-temperature side heat medium flowing through the low-temperature side circuit 60.

[0038] The low-temperature side radiator 62 absorbs heat from the outside air by exchanging heat between the low-temperature side heat medium that has passed through the device evaporators 18, 20 and the outside air outside the vehicle cabin. The low-temperature side radiator 62 is disposed, for example, on the front side in the traveling direction of the vehicle together with the high-temperature side radiator 52. The high-temperature side radiator 52 and the low-temperature side radiator 62 are disposed so as to be lined up in series in this order in the flow direction of the outside air. The high-temperature side radiator 52 and the low-temperature side radiator 62 are connected to each other by a common heat transfer fin (not shown) so as to be able to transfer heat between them.

[0039] The heat generating device 63 is arranged in parallel with the low-temperature side radiator 62 in the low-temperature side circuit 60. The heat generating device 63 is an in-vehicle device including a battery BT. The heat generating device 63 is arranged so as to be able to exchange heat with the low-temperature side heat medium. The heat generating device 63 is maintained at an appropriate temperature by dissipating heat to the low-temperature side heat medium. In other words, the low-temperature side circuit 60 absorbs heat from the heat generating device 63 via the low-temperature side heat medium. Note that the in-vehicle device constituting the heat generating device 63 may be different from that described above.

[0040] The second flow path switching valve 64 functions as a flow path switching unit that switches the flow path of the low-temperature side heat medium. The second flow path switching valve 64 is provided at a branching unit that branches the flow path of the low-temperature side heat medium in the low-temperature side circuit 60 into a flow path on the low-temperature side radiator 62 side and a flow path on the heat-generating device 63 side. The second flow path switching valve 64 is configured as an electromagnetic three-way valve, and its operation is controlled by a control signal output from the control unit 100.

[0041] The low-temperature side reserve tank 65 is a tank for storing surplus low-temperature side heat medium. The low-temperature side reserve tank 65 is disposed in the flow path from the junction of the flow path of the low-temperature side radiator 62 and the flow path of the heat generating device 63 to the inlet of the low-temperature side pump 61.

[0042] The first equipment evaporator 18 and the second equipment evaporator 20 are connected in parallel between the low-temperature side reserve tank 65 and the low-temperature side pump 61 so that the low-temperature side heat medium is distributed to the first equipment evaporator 18 and the second equipment evaporator 20. A third flow path switching valve 66 is provided at a branching section where the flow path of the low-temperature side heat medium branches into a flow path on the first equipment evaporator 18 side and a flow path on the second equipment evaporator 20 side.

[0043] The third flow path switching valve 66 functions as a flow path switching unit that switches the flow path of the low-temperature side heat medium. The third flow path switching valve 66 is configured as an electromagnetic three-way valve, and the operation of the third flow path switching valve 66 is controlled by a control signal output from the control unit 100.

[0044] The heat exchange system 1 thus configured includes a control unit 100 for controlling various components. The control unit 100 is composed of a microcomputer including a processor and memory and its peripheral circuits. The control unit 100 performs various calculations and processes based on a control program stored in the memory. The memory of the control unit 100 is composed of a non-transient substantial storage medium.

[0045] Various operation switches (not shown) are connected to the input side of the control unit 100, and operation signals of the various operation switches are input. The various operation switches include an air conditioner switch, a room temperature adjustment switch, etc. The air conditioner switch is a switch that sets whether or not the air is cooled by the air conditioning unit 40. The room temperature adjustment switch is a switch that sets the set temperature inside the vehicle cabin.

[0046] Further, a group of sensors for air conditioning control and a group of sensors for equipment temperature control are connected to the input side of the control unit 100. The group of sensors for air conditioning control includes, for example, a first superheat sensor provided on the refrigerant outlet side of the air conditioning evaporator 15, a second superheat sensor provided on the refrigerant outlet side of the first equipment evaporator 18, and a third superheat sensor provided on the refrigerant outlet side of the second equipment evaporator 20. The first superheat sensor is a sensor that detects the superheat degree SH1 of the refrigerant that has passed through the air conditioning evaporator 15. The second superheat sensor is a sensor that detects the superheat degree SH2 of the refrigerant that has passed through the first equipment evaporator 18. The third superheat sensor is a sensor that detects the superheat degree SH3 of the refrigerant that has passed through the second equipment evaporator 20. Each superheat sensor is, for example, a pressure-temperature sensor that detects the pressure and temperature of the refrigerant.

[0047] The output side of the control unit 100 is connected to the compressor 11, the first pressure reducing valve 14, the second pressure reducing valve 17, the third pressure reducing valve 19, the high temperature side pump 51, the electric heater 53, the first flow path switching valve 55, the low temperature side pump 61, the second flow path switching valve 64, the third flow path switching valve 66, etc. The control unit 100 controls the operation of various controlled devices based on the sensor outputs of the sensor group for air conditioning control and the sensor group for device temperature adjustment, the operation signals of various operation switches, etc.

[0048] The control unit 100 calculates the amount of air to be blown into the vehicle cabin based on the set temperature, outside air temperature, inside air temperature, amount of solar radiation, etc., and controls the refrigerant discharge capacity of the compressor 11 so that the temperature of the air to be blown into the vehicle cabin approaches a target outlet temperature. In addition, when the refrigerant flows through each of the evaporators 15, 18, 20, the control unit 100 controls the operation of each of the pressure reducing valves 14, 17, 19 so that the refrigerant at the refrigerant outlet side of each of the evaporators 15, 18, 20 has a desired degree of superheat SH.

[0049] The control unit 100 of this embodiment switches the operation mode of the heat exchange system 1 based on the sensor outputs of the group of sensors for air conditioning control and the group of sensors for equipment temperature control, operation signals of various operation switches, etc. The control unit 100, for example, calculates a target blowing temperature of the conditioned air blown from the air conditioning unit 40 into the vehicle cabin, and performs cooling, heating, and dehumidifying and heating of the vehicle cabin based on the target blowing temperature, etc. The control unit 100 also cools the heat-generating equipment 63 based on the monitoring results of the temperature of the heat-generating equipment 63, etc.

[0050] In this embodiment, the comparative cycle is a refrigeration cycle 10 without the third pressure reducing valve 19 and the second equipment evaporator 20. The comparative cycle has two heat absorbers, namely, the air conditioning evaporator 15 that absorbs heat from the blown air sent to the space to be air-conditioned, and the first equipment evaporator 18 that absorbs heat from the heat absorbing medium that absorbs heat from the heat generating device 63 or the external space.

[0051] In the refrigeration cycle 10 of the present embodiment and the comparative cycle, in order to respond to various situations, it is important to ensure an adjustment range of the distribution between the heat absorption capacity of absorbing heat from the blown air and the heat absorption capacity of absorbing heat from the heat absorption medium. In particular, in the future, with the spread of electric vehicles, the heat generation of the battery BT is expected to increase. As the heat generation of the battery BT increases, the above-mentioned problem of the capacity distribution becomes more prominent, so it becomes important to build a system with a wide adjustment range of the above-mentioned capacity distribution.

[0052] As a countermeasure to this, for example, it is possible to change the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the heat absorption medium by increasing or decreasing the opening area of ​​one of the first pressure reducing valve 14 and the second pressure reducing valve 17 in the comparison cycle.

[0053] For example, in an air-conditioning priority scene in which cooling the vehicle cabin takes priority over absorbing heat from the heat-generating device 63 or the external space, it is possible to increase the opening area of ​​the second pressure reducing valve 17 to increase the flow rate of the refrigerant flowing through the air-conditioning evaporator 15. In this embodiment, the air-conditioning priority scene corresponds to the "first scene."

[0054] However, in such a capacity distribution adjustment method, the flow rate of the refrigerant flowing into the first equipment evaporator 18 decreases, so that the degree of superheat SH2 of the refrigerant at the refrigerant outlet side of the first equipment evaporator 18 becomes excessive, for example, as shown in Fig. 3. In this case, the degree of superheat SH of the refrigerant sucked into the compressor 11 also becomes excessive, and there is a risk that the temperature of the high-pressure refrigerant discharged from the compressor 11 exceeds the allowable temperature or that it becomes difficult for refrigerating machine oil to return to the compressor 11.

[0055] Also, for example, in a heat absorption priority scene in which heat absorption from the heat generating device 63 or the external space takes priority over cooling the vehicle interior, it is possible to increase the opening area of ​​the first pressure reducing valve 14 and increase the flow rate of the refrigerant flowing through the first device evaporator 18. In this embodiment, the heat absorption priority scene corresponds to the "second scene."

[0056] However, in such a capacity distribution adjustment method, the flow rate of the refrigerant flowing into the air-conditioning evaporator 15 is reduced, and as shown in FIG. 4, for example, the degree of superheat SH1 of the refrigerant at the refrigerant outlet side of the air-conditioning evaporator 15 becomes excessive. In this case, the degree of superheat SH of the refrigerant drawn into the compressor 11 also becomes excessive, and there is a risk that the temperature of the high-pressure refrigerant discharged from the compressor 11 exceeds the allowable temperature or that it becomes difficult for the refrigerating machine oil to return to the compressor 11. In addition, if the opening area of ​​the first pressure reducing valve 14 is increased, as shown in FIG. 5, the gas-phase refrigerant flows on the side close to the refrigerant outlet of the air-conditioning evaporator 15. At the location where this gas-phase refrigerant flows, heat exchange occurs due to sensible heat, and the temperature distribution of the blown air is likely to expand, so there is a risk that the comfort in the vehicle cabin may deteriorate.

[0057] Because of this trade-off, the above-mentioned method for adjusting capacity distribution has a narrow range of capacity distribution adjustment, and it is difficult to appropriately change the distribution between the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium.

[0058] Taking these factors into consideration, the heat exchange system 1 of this embodiment is configured to adjust the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the low-temperature side heat medium by changing the heat exchange amount in the second equipment evaporator 20.

[0059] In the heat exchange system 1 of this embodiment, the control unit 100 controls the third pressure reducing valve 19 and the third flow path switching valve 66 to adjust the flow rates of the refrigerant and low-temperature side heat medium passing through the second device evaporator 20, thereby changing the heat exchange amount in the second device evaporator 20. The control unit 100 of this embodiment includes a capacity adjustment unit 100a that adjusts the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium.

[0060] When an air conditioning priority scene occurs, the control unit 100 reduces the amount of refrigerant supplied to the second equipment evaporator 20 and increases the flow rate of refrigerant flowing into the air conditioning evaporator 15, thereby increasing the amount of heat exchange between the refrigerant and the blown air.

[0061] For example, when the air conditioning priority scene is reached, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to a throttled state and controls the third pressure reducing valve 19 to a fully closed state, as shown in Fig. 6. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the air conditioning evaporator 15 has a desired degree of superheat SH, and controls the second pressure reducing valve 17 so that the refrigerant that has passed through the first equipment evaporator 18 has a desired degree of superheat SH. In addition, the control unit 100 controls the third flow path switching valve 66 to a half-open state so that the low-temperature side heat medium flows to the first equipment evaporator 18 and does not flow to the second equipment evaporator 20.

[0062] 7, the degree of superheat SH1 of the refrigerant at the refrigerant outlet side of the air conditioning evaporator 15 and the degree of superheat SH2 of the refrigerant at the refrigerant outlet side of the first equipment evaporator 18 are each maintained at an appropriate state. This ensures comfort in the vehicle cabin and protects the compressor 11.

[0063] In addition, in the air-conditioning priority scene, the flow rate of the refrigerant flowing into the air-conditioning evaporator 15 increases, increasing the amount of heat exchanged between the refrigerant and the blown air, and increasing the amount of heat absorbed from the blown air. Also, as shown in Fig. 8, the refrigerant and low-temperature side heat medium do not flow into the second equipment evaporator 20, so the amount of heat absorbed from the low-temperature side heat medium decreases accordingly.

[0064] In this way, in an air conditioning priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that cooling inside the vehicle cabin is given priority over heat absorption from the heat generating device 63 or the external space.

[0065] On the other hand, when the heat absorption priority scene is reached, the control unit 100 controls the first pressure reducing valve 14, the second pressure reducing valve 17, and the third pressure reducing valve 19 to be in a throttled state. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the air conditioning evaporator 15 has a desired degree of superheat SH, and controls the second pressure reducing valve 17 and the third pressure reducing valve 19 so that the refrigerant that has passed through the equipment evaporators 18 and 20 has a desired degree of superheat SH. The control unit 100 also controls the third flow path switching valve 66 to be in a fully open state so that the low-temperature side heat medium flows to both the first equipment evaporator 18 and the second equipment evaporator 20.

[0066] In this case, as shown in Fig. 9, the degree of superheat SH1 of the refrigerant at the refrigerant outlet side of the air conditioning evaporator 15, the degree of superheat SH2 of the refrigerant at the refrigerant outlet side of the first equipment evaporator 18, and the degree of superheat SH3 of the refrigerant at the refrigerant outlet side of the second equipment evaporator 20 are each maintained at an appropriate state. This ensures comfort in the vehicle cabin and protects the compressor 11. Note that in Fig. 9, the refrigerant pressures in the second equipment evaporator 20 and the first equipment evaporator 18 are different pressures because the equipment evaporators 18 and 20 are illustrated on the Mollier diagram, but in reality, they are approximately the same pressure.

[0067] In addition, as shown in FIG. 10, in the heat absorption priority scene, heat exchange between the refrigerant and the low-temperature side heat medium is performed in two heat absorbers, namely the evaporator 18 for the first equipment and the evaporator 20 for the second equipment, so that the amount of heat absorbed from the low-temperature side heat medium increases.

[0068] In this way, in an equipment priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that heat absorption from the heat-generating equipment 63 or the external space is given priority over air conditioning inside the vehicle cabin.

[0069] The heat exchange system 1 described above is provided with the second device evaporator 20 as a heat absorbing heat exchanger that adjusts the amount of heat absorbed from the low-pressure side heat medium by exchanging heat between the refrigerant and a predetermined fluid. The heat exchange system 1 is configured to adjust the distribution of the heat absorption capacity of absorbing heat from the blown air and the heat absorption capacity of absorbing heat from the low-pressure side medium by changing the amount of heat exchanged in the second device evaporator 20.

[0070] According to this, the amount of heat absorbed from the low-temperature side heat medium is adjusted by two heat absorbers, the first device evaporator 18 and the second device evaporator 20, so that the adjustment range of the heat absorption capacity for absorbing heat from the low-temperature side heat medium can be increased. The heat absorption capacity for absorbing heat from the blown air changes in response to the increase or decrease in the heat absorption capacity of the low-temperature side heat medium.

[0071] Therefore, according to the heat exchange system 1 of the present disclosure, it is possible to ensure an adjustment range for the distribution between the heat absorption capacity of absorbing heat from the air blown into the space to be air-conditioned and the heat absorption capacity of absorbing heat from the low-temperature side heat medium. In particular, by increasing the adjustment range of the heat absorption capacity of the low-temperature side heat medium, there is an advantage that it becomes easier to appropriately adjust the temperature of heat-generating devices 63 that generate a large amount of heat, such as batteries BT.

[0072] Moreover, the heat exchange system 1 of this embodiment has the following features.

[0073] (1) The heat exchange system 1 includes a third pressure reducing valve 19 arranged in parallel with the first pressure reducing valve 14 and the second pressure reducing valve 17 downstream of the condenser 12, and a second equipment evaporator 20 that evaporates the refrigerant reduced in pressure by the third pressure reducing valve 19 by heat exchange with a low-temperature side heat medium. The control unit 100 of the heat exchange system 1 adjusts the distribution of the heat absorption capacity of absorbing heat from the blown air and the heat absorption capacity of absorbing heat from the heat absorption medium by increasing the amount of refrigerant supplied to the second equipment evaporator 20 or decreasing the amount of refrigerant supplied to the second equipment evaporator 20.

[0074] According to this, since the amount of heat absorbed from the low-temperature side heat medium can be increased or decreased by increasing or decreasing the amount of refrigerant supplied to the second equipment evaporator 20, the adjustment range of the heat absorption capacity for absorbing heat from the low-temperature side heat medium can be increased. In addition, the occurrence of temperature distribution in the air-conditioning evaporator 15 and the temperature of the refrigerant discharged from the compressor 11 are suppressed.

[0075] (2) Specifically, when the heat absorption priority scene occurs, the control unit 100 supplies refrigerant to the second device evaporator 20 to increase the amount of heat exchanged between the refrigerant and the low-temperature side heat medium. Also, when the air conditioning priority scene occurs, the control unit 100 decreases the amount of refrigerant supplied to the second device evaporator 20 to increase the amount of heat exchanged between the refrigerant and the blown air. This makes it possible to appropriately adjust the distribution between the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium according to each of the air conditioning priority scene and the heat absorption priority scene.

[0076] (3) In the low-temperature side circuit 60, the first device evaporator 18 and the second device evaporator 20 are connected in parallel so that the low-temperature side heat medium is distributed to the first device evaporator 18 and the second device evaporator 20. Then, the control unit 100 supplies the low-temperature side heat medium to the second device evaporator 20 in the heat absorption priority scene to increase the amount of heat exchange between the refrigerant and the low-temperature side heat medium. Also, the control unit 100 reduces the amount of low-temperature side heat medium supplied to the second device evaporator 20 in the air conditioning priority scene. In this way, if the amount of low-temperature side heat medium supplied to the second device evaporator 20 is reduced in the air conditioning priority scene, the flow rate of the low-temperature side heat medium flowing into the first device evaporator 18 increases in the air conditioning priority scene, making it easier to ensure the heat absorption capacity to absorb heat from the low-temperature side heat medium.

[0077] (First Modification of the First Embodiment) Although the third flow path switching valve 66 in the first embodiment is exemplified as being configured with one electromagnetic three-way valve, the present invention is not limited thereto. For example, as shown in Fig. 11, the third flow path switching valve 66 may be configured with a first opening / closing valve 66a arranged upstream of the first equipment evaporator 18 and a second opening / closing valve 66b arranged upstream of the second equipment evaporator 20.

[0078] In the first embodiment, the third pressure reducing valve 19 is exemplified as a variable throttle with a full closing function, but is not limited thereto. As long as the supply of refrigerant to the second equipment evaporator 20 can be stopped by an on-off valve or the like, the third pressure reducing valve 19 may be configured as, for example, a mechanical expansion valve. This also applies to the first pressure reducing valve 14 and the second pressure reducing valve 17. The heat exchange system 1 may be configured not to stop the supply of refrigerant to the air conditioning evaporator 15 and the first equipment evaporator 18. This also applies to the following embodiments.

[0079] (Second Modification of the First Embodiment) In the first embodiment, the low-temperature side circuit 60 has the first equipment evaporator 18 and the second equipment evaporator 20 connected in parallel so that the low-temperature side heat medium is distributed to the first equipment evaporator 18 and the second equipment evaporator 20, but is not limited to this.

[0080] 12, the low-temperature side circuit 60 may be configured such that the first device evaporator 18 and the second device evaporator 20 are connected in series so that the low-temperature side heat medium flows from one of the first device evaporator 18 and the second device evaporator 20 to the other. This also makes it possible to appropriately adjust the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium according to the air conditioning priority scene and the heat absorption priority scene, respectively.

[0081] (Third Modification of the First Embodiment) In the refrigeration cycle 10 of the first embodiment, the third pressure reducing valve 19 is arranged in parallel with the first pressure reducing valve 14 and the second pressure reducing valve 17, but is not limited thereto. For example, as shown in Fig. 13, the refrigeration cycle 10 may be configured such that the second equipment evaporator 20 is connected to the refrigerant outlet side of the second pressure reducing valve 17 so as to be in parallel with the first equipment evaporator 18. In this case, an opening / closing valve Vs for controlling the supply of refrigerant to the second equipment evaporator 20 may be provided instead of the third pressure reducing valve 19.

[0082] Second embodiment Next, a second embodiment will be described with reference to Figures 14 to 17. In this embodiment, differences from the first embodiment will be mainly described.

[0083] 14, in the refrigeration cycle 10, the third pressure reducing valve 19 is omitted, and the second equipment evaporator 20A is disposed downstream of the air conditioning evaporator 15 so as to be in series with the air conditioning evaporator 15. In this embodiment, the second equipment evaporator 20A corresponds to the "heat absorption heat exchanger."

[0084] Here, if the air conditioning evaporator 15 and the second equipment evaporator 20A are simply connected in series, the refrigerant passing through the air conditioning evaporator 15 and the refrigerant passing through the second equipment evaporator 20A will be homogenized, and there is a risk that the pressure of the refrigerant passing through the air conditioning evaporator 15 will decrease more than necessary.

[0085] Considering this, the refrigeration cycle 10 of this embodiment is provided with an evaporation pressure regulating valve 16 between the air conditioning evaporator 15 and the second equipment evaporator 20A. This allows the evaporation pressure regulating valve 16 to regulate the refrigerant pressure of the air conditioning evaporator 15.

[0086] In the refrigeration cycle 10 configured as above, the second equipment evaporator 20A is connected in series to the air conditioning evaporator 15, and when the refrigerant is supplied to the air conditioning evaporator 15, the refrigerant also flows into the second equipment evaporator 20A. Therefore, in the refrigeration cycle 10 of this embodiment, the supply of the refrigerant to the second equipment evaporator 20A cannot be stopped freely. On the other hand, the low-temperature side circuit 60 can supply the low-temperature side heat medium to the second equipment evaporator 20A or stop the supply of the low-temperature side heat medium to the second equipment evaporator 20A by the third flow path switching valve 66.

[0087] Taking these factors into consideration, the heat exchange system 1 of this embodiment changes the amount of heat exchange in the second equipment evaporator 20A by adjusting the flow rate of the low-temperature side heat medium passing through the second equipment evaporator 20A through the control of the third flow path switching valve 66 by the control unit 100.

[0088] For example, when the air conditioning priority scene is reached, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to a throttling state as shown in Fig. 15. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the air conditioning evaporator 15 has a desired degree of superheat SH, and controls the second pressure reducing valve 17 so that the refrigerant that has passed through the first equipment evaporator 18 has a desired degree of superheat SH. In addition, the control unit 100 controls the third flow path switching valve 66 to a half-open state so that the low-temperature side heat medium flows to the first equipment evaporator 18 and does not flow to the second equipment evaporator 20A.

[0089] In this case, as shown in Fig. 16, the degree of superheat SH1 of the refrigerant at the refrigerant outlet side of the air conditioning evaporator 15 and the degree of superheat SH2 of the refrigerant at the refrigerant outlet side of the first equipment evaporator 18 are each maintained in an appropriate state. This ensures comfort in the vehicle cabin and protects the compressor 11.

[0090] In addition, in the air conditioning priority scene, the refrigerant and the low-temperature side heat medium are not exchanged in the second device evaporator 20A, so the amount of heat exchanged between the refrigerant and the blown air increases, and the amount of heat absorbed from the blown air increases. Note that, since the low-temperature side heat medium does not flow into the second device evaporator 20A, the amount of heat absorbed from the low-temperature side heat medium decreases accordingly.

[0091] In this way, in an air conditioning priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that cooling inside the vehicle cabin is given priority over heat absorption from the heat generating device 63 or the external space.

[0092] On the other hand, when the heat absorption priority scene is reached, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to the throttled state as shown in Fig. 15. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant passing through the second equipment evaporator 20A has a desired superheat degree SH, and controls the second pressure reducing valve 17 so that the refrigerant passing through the first equipment evaporator 18 has a desired superheat degree SH. The control unit 100 also controls the third flow path switching valve 66 to the fully open state so that the low-temperature side heat medium flows through both the first equipment evaporator 18 and the second equipment evaporator 20A.

[0093] In this case, as shown in Fig. 17, the degree of superheat SH2 of the refrigerant at the refrigerant outlet side of the first equipment evaporator 18 and the degree of superheat SH3 of the refrigerant at the refrigerant outlet side of the second equipment evaporator 20A are each maintained at an appropriate state. This ensures comfort in the vehicle cabin and protects the compressor 11. Note that in Fig. 17, the refrigerant pressure in the second equipment evaporator 20A and the refrigerant pressure in the first equipment evaporator 18 are different pressures because the equipment evaporators 18 and 20A are illustrated on a Mollier diagram, but in reality, the refrigerant pressures are approximately the same.

[0094] In addition, in the heat absorption priority scene, heat exchange between the refrigerant and the low-temperature side heat medium is performed in two heat absorbers, namely the first equipment evaporator 18 and the second equipment evaporator 20A, so the amount of heat absorbed from the low-temperature side heat medium increases.

[0095] In this way, in an equipment priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that heat absorption from the heat-generating equipment 63 or the external space is given priority over air conditioning inside the vehicle cabin.

[0096] The rest is the same as in the first embodiment. The heat exchange system 1 of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a configuration common to the first embodiment or an equivalent configuration.

[0097] Moreover, the heat exchange system 1 of this embodiment has the following features.

[0098] (1) The refrigeration cycle 10 includes a second equipment evaporator 20A that evaporates the refrigerant that has passed through the air conditioning evaporator 15 by heat exchange with a low-temperature side heat medium. The control unit 100 adjusts the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium by increasing or decreasing the amount of low-temperature side heat medium supplied to the second equipment evaporator 20A. This allows the amount of heat absorbed from the low-temperature side heat medium to be increased or decreased, thereby making it possible to increase the adjustment range of the heat absorption capacity for absorbing heat from the low-temperature side heat medium.

[0099] (2) When the air conditioning priority scene occurs, the control unit 100 increases the amount of heat exchange between the refrigerant and the blown air by supplying the low-temperature side heat medium to the first device evaporator 18 while reducing the supply of the low-temperature side heat medium to the second device evaporator 20A. When the heat absorption priority scene occurs, the control unit 100 supplies the low-temperature side heat medium to both the first device evaporator 18 and the second device evaporator 20A to increase the amount of heat exchange between the refrigerant and the low-temperature side heat medium. This makes it possible to appropriately adjust the distribution between the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium according to the air conditioning priority scene and the heat absorption priority scene.

[0100] (3) Between the air conditioning evaporator 15 and the second equipment evaporator 20A, an evaporation pressure regulating valve 16 is provided to regulate the pressure of the refrigerant in the air conditioning evaporator 15. This allows the evaporation pressure regulating valve 16 to maintain the refrigerant passing through the air conditioning evaporator 15 at a higher pressure than the refrigerant passing through the second equipment evaporator 20A. As a result, the air can be cooled to a desired temperature in the air conditioning evaporator 15.

[0101] (First modified example of the second embodiment) In the heat exchange system 1 of the second embodiment, the flow rate of the low-temperature side heat medium passing through the evaporator 20A for the second equipment is adjusted by the control of the third flow path switching valve 66 by the control unit 100, thereby changing the amount of heat exchange in the evaporator 20A for the second equipment, but this is not limited to this.

[0102] The heat exchange system 1 may be configured to change the amount of heat absorbed from the low-temperature side heat medium by adjusting the flow rate of the refrigerant passing through the first equipment evaporator 18 through control of the second pressure reducing valve 17 by the control unit 100.

[0103] For example, when an air conditioning priority scene occurs, the control unit 100 controls the first pressure reducing valve 14 to a throttled state and the second pressure reducing valve 17 to a fully closed state as shown in Fig. 18. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the air conditioning evaporator 15 has a desired degree of superheat SH. In addition, the control unit 100 controls the third flow path switching valve 66 to a half-open state so that the low-temperature side heat medium flows to the second equipment evaporator 20A and does not flow to the first equipment evaporator 18.

[0104] In this case, the degree of superheat SH1 of the refrigerant at the refrigerant outlet side of the air-conditioning evaporator 15 is maintained at an appropriate state. This ensures comfort in the vehicle cabin and protects the compressor 11. In addition, in the air-conditioning priority scene, the first device evaporator 18 does not exchange heat between the refrigerant and the low-temperature side heat medium, so the amount of heat exchanged between the refrigerant and the blown air increases, and the amount of heat absorbed from the blown air increases. In addition, since the low-temperature side heat medium does not flow into the first device evaporator 18, the amount of heat absorbed from the low-temperature side heat medium decreases accordingly.

[0105] In this way, in an air conditioning priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that cooling inside the vehicle cabin is given priority over heat absorption from the heat generating device 63 or the external space.

[0106] On the other hand, when the heat absorption priority scene is reached, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to be in a throttled state. Also, the control unit 100 controls the third flow path switching valve 66 to be in a fully open state so that the low-temperature side heat medium flows to both the first device evaporator 18 and the second device evaporator 20A. In this case, the same effect as in the second embodiment can be obtained.

[0107] (Second modified example of the second embodiment) Although the third flow path switching valve 66 in the second embodiment is exemplified as being configured with one electromagnetic three-way valve, the present invention is not limited thereto. For example, as shown in Fig. 19, the third flow path switching valve 66 may be configured with a first opening / closing valve 66a arranged upstream of the first equipment evaporator 18 and a second opening / closing valve 66b arranged upstream of the second equipment evaporator 20A.

[0108] Third embodiment Next, a third embodiment will be described with reference to Figures 20 to 22. In this embodiment, differences from the second embodiment will be mainly described.

[0109] In the low-temperature side circuit 60 of this embodiment, for example, as shown in FIG. 20, the first equipment evaporator 18 and the second equipment evaporator 20A are connected in series so that the low-temperature side heat medium flows from one of the first equipment evaporator 18 and the second equipment evaporator 20A to the other.

[0110] In the heat exchange system 1 configured as above, the device evaporators 18, 20A are connected in series in the low-temperature side circuit 60, and when the low-temperature side heat medium is supplied to one of the device evaporators 18, 20A, the low-temperature side heat medium also flows into the other. For this reason, the low-temperature side circuit 60 of this embodiment cannot freely stop the supply of the low-temperature side heat medium to the second device evaporator 20A.

[0111] In consideration of these, the heat exchange system 1 of this embodiment is configured to adjust the distribution of the heat absorption capacity of absorbing heat from the blown air and the heat absorption capacity of absorbing heat from the low-temperature side heat medium by changing the heat exchange amount in the first equipment evaporator 18. The heat exchange system 1 changes the heat exchange amount in the first equipment evaporator 18 by adjusting the flow rate of the low-temperature side heat medium passing through the first equipment evaporator 18 through the control of the second pressure reducing valve 17 by the control unit 100.

[0112] In this embodiment, when an air conditioning priority scene occurs, the control unit 100 reduces the amount of refrigerant supplied to the first equipment evaporator 18 and increases the flow rate of refrigerant flowing into the air conditioning evaporator 15, thereby increasing the amount of heat exchange between the refrigerant and the blown air.

[0113] For example, when an air conditioning priority scene occurs, the control unit 100 controls the first pressure reducing valve 14 to a throttled state and controls the second pressure reducing valve 17 to a fully closed state as shown in Fig. 21. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the second equipment evaporator 20A has a desired degree of superheat SH.

[0114] In this case, as shown in Fig. 22, the degree of superheat SH2 of the refrigerant at the refrigerant outlet side of the second equipment evaporator 20A is maintained at an appropriate state. This ensures comfort in the vehicle cabin and protects the compressor 11. In addition, in the air-conditioning priority scene, the flow rate of the refrigerant flowing into the air-conditioning evaporator 15 increases, increasing the amount of heat exchanged between the refrigerant and the blown air, and increasing the amount of heat absorbed from the blown air. Also, since the refrigerant and low-temperature side heat medium do not flow into the first equipment evaporator 18, the amount of heat absorbed from the low-temperature side heat medium decreases accordingly.

[0115] In this way, in an air conditioning priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that cooling inside the vehicle cabin is given priority over heat absorption from the heat generating device 63 or the external space.

[0116] On the other hand, when the heat absorption priority scene is reached, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to be in a throttled state as shown in Fig. 21. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the second equipment evaporator 20A has a desired degree of superheat SH, and controls the second pressure reducing valve 17 so that the refrigerant that has passed through the first equipment evaporator 18 has a desired degree of superheat SH. In this case, the same effects as those of the second embodiment can be obtained.

[0117] The rest is the same as in the second embodiment. The heat exchange system 1 of this embodiment can obtain the same effects as in the second embodiment, which are achieved by a common configuration with the second embodiment or an equivalent configuration.

[0118] Moreover, the heat exchange system 1 of this embodiment has the following features.

[0119] (1) The heat exchange system 1 adjusts the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium by increasing or decreasing the amount of refrigerant supplied to the first equipment evaporator 18. This allows the amount of heat absorbed from the low-temperature side heat medium to be increased or decreased by increasing or decreasing the amount of refrigerant supplied to the first equipment evaporator 18, so that the adjustment range of the heat absorption capacity for absorbing heat from the low-temperature side heat medium can be increased.

[0120] (2) When the air conditioning priority scene is reached, the control unit 100 increases the amount of heat exchange between the refrigerant and the blown air by reducing the amount of refrigerant supplied to the first equipment evaporator 18 while supplying refrigerant to the second equipment evaporator 20A. When the equipment priority scene is reached, the control unit 100 increases the amount of heat exchange between the refrigerant and the low-temperature side heat medium by supplying refrigerant to both the first equipment evaporator 18 and the second equipment evaporator 20A. This makes it possible to appropriately adjust the distribution between the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium according to the air conditioning priority scene and the equipment priority scene.

[0121] (Fourth embodiment) Next, a fourth embodiment will be described with reference to Fig. 23 to Fig. 25. In this embodiment, differences from the first embodiment will be mainly described.

[0122] 23, the third pressure reducing valve 19 and the second device evaporator 20 are omitted from the refrigeration cycle 10. Instead, an internal heat exchanger 21 that exchanges heat between the high-pressure refrigerant and the low-pressure refrigerant flowing in the cycle is added to the refrigeration cycle 10. The internal heat exchanger 21 has a high-pressure flow path portion 211 through which the high-pressure refrigerant passes and a low-pressure flow path portion 212 through which the low-pressure refrigerant passes.

[0123] The high-pressure flow path portion 211 is disposed in a refrigerant path from a refrigerant branching portion provided downstream of the receiver portion 13 to the second pressure reducing valve 17. Therefore, the refrigerant that has passed through the high-pressure flow path portion 211 flows to the first pressure reducing valve 14.

[0124] The low-pressure flow path portion 212 is disposed in a refrigerant path from the evaporation pressure regulating valve 16 to a refrigerant junction portion on the refrigerant suction side of the compressor 11. Therefore, the refrigerant that has passed through the air-conditioning evaporator 15 flows into the low-pressure flow path portion 212.

[0125] In the refrigeration cycle 10 of the present embodiment, the internal heat exchanger 21 is disposed, so that, for example, as shown in Fig. 24, the refrigerant flowing through the high-pressure flow passage portion 211 is supercooled by heat exchange with the refrigerant flowing through the low-pressure flow passage portion 212. This increases the enthalpy difference before and after the first device evaporator 18, thereby ensuring a sufficient amount of heat absorption from the low-temperature side heat medium.

[0126] The heat exchange system 1 configured in this manner adjusts the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-temperature side heat medium by changing the heat exchange amount between the low-pressure refrigerant and the high-pressure refrigerant in the internal heat exchanger 21. The heat exchange system 1 changes the heat exchange amount between the low-pressure refrigerant and the high-pressure refrigerant in the internal heat exchanger 21 by changing the opening area of ​​the second pressure reducing valve 17 using the control unit 100. In this embodiment, the internal heat exchanger 21 corresponds to the "heat exchanger for absorbing heat."

[0127] For example, when the air conditioning priority scene occurs, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to a throttling state as shown in Fig. 25. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the low pressure flow passage portion 212 has a desired degree of superheat SH. The control unit 100 also controls the second pressure reducing valve 17 so that the opening area of ​​the second pressure reducing valve 17 is smaller than a predetermined reference area. The reference area is set to the opening area of ​​the second pressure reducing valve 17 when the second pressure reducing valve 17 is controlled so that the refrigerant that has passed through the first equipment evaporator 18 has a desired degree of superheat SH, for example.

[0128] In this way, in the air conditioning priority scene, the opening area of ​​the second pressure reducing valve 17 is reduced, so that the flow rate of the refrigerant flowing into the first equipment evaporator 18 decreases and the flow rate of the refrigerant flowing into the air conditioning evaporator 15 increases. In addition, when the opening area of ​​the second pressure reducing valve 17 is reduced, the flow rate of the refrigerant flowing into the internal heat exchanger 21 decreases, and the heat exchange amount in the internal heat exchanger 21 decreases, so that the enthalpy difference before and after the first equipment evaporator 18 decreases. As a result, the heat absorption capacity of absorbing heat from the low pressure side medium can be sufficiently reduced. And when the heat absorption capacity of absorbing heat from the low pressure side medium becomes sufficiently reduced, the heat absorption capacity of absorbing heat from the blown air becomes sufficiently large accordingly.

[0129] Therefore, in an air conditioning priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that cooling in the vehicle cabin is given priority over heat absorption from the heat generating device 63 or the external space.

[0130] On the other hand, when the equipment priority scene is reached, for example, the control unit 100 controls the first pressure reducing valve 14 and the second pressure reducing valve 17 to a throttling state as shown in Fig. 25. Specifically, the control unit 100 controls the first pressure reducing valve 14 so that the refrigerant that has passed through the low-pressure flow path portion 212 has a desired superheat degree SH. In addition, the control unit 100 controls the second pressure reducing valve 17 so that the opening area of ​​the second pressure reducing valve 17 is larger than a predetermined reference area.

[0131] In this way, in the equipment priority scene, the opening area of ​​the second pressure reducing valve 17 is increased, so that the flow rate of the refrigerant flowing into the first equipment evaporator 18 increases and the flow rate of the refrigerant flowing into the air conditioning evaporator 15 decreases. In addition, when the opening area of ​​the second pressure reducing valve 17 is increased, the flow rate of the refrigerant flowing into the internal heat exchanger 21 increases, and the heat exchange amount in the internal heat exchanger 21 increases, so that the enthalpy difference before and after the first equipment evaporator 18 increases. As a result, the heat absorption capacity for absorbing heat from the low-pressure side medium can be sufficiently increased.

[0132] Therefore, in an equipment priority scene, the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium can be appropriately allocated so that heat absorption from the heat-generating equipment 63 or the external space is given priority over air conditioning inside the vehicle cabin.

[0133] The rest is the same as in the first embodiment. The heat exchange system 1 of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a configuration common to the first embodiment or an equivalent configuration.

[0134] Moreover, the heat exchange system 1 of this embodiment has the following features.

[0135] (1) The heat exchange system 1 is provided with an internal heat exchanger 21 as a heat absorption heat exchanger that adjusts the amount of heat absorbed from the low-pressure side heat medium by exchanging heat between the refrigerant and a specified fluid. The heat exchange system 1 adjusts the distribution of the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the low-pressure side heat medium by changing the opening area of ​​the second pressure reducing valve 17 to change the heat exchange amount of the internal heat exchanger 21 in addition to the flow rate of the refrigerant passing through the first equipment evaporator 18. With this configuration, it is possible to increase the adjustment range of the heat absorption capacity for absorbing heat from the low-pressure side heat medium.

[0136] (2) Specifically, when the air conditioning priority scene occurs, the control unit 100 reduces the opening area of ​​the second pressure reducing valve 17 to increase the flow rate of refrigerant flowing through the air conditioning evaporator 15 and reduce the heat exchange amount of the internal heat exchanger 21. Also, when the heat absorption priority scene occurs, the control unit 100 increases the opening area of ​​the second pressure reducing valve 17 to increase the flow rate of refrigerant flowing through the first equipment evaporator 18 and increase the heat exchange amount of the internal heat exchanger 21. This makes it possible to appropriately adjust the distribution between the heat absorption capacity for absorbing heat from the blown air and the heat absorption capacity for absorbing heat from the heat absorption medium according to each of the air conditioning priority scene and the heat absorption priority scene.

[0137] (Modification of the fourth embodiment) In the refrigeration cycle 10 of the first embodiment, the second device evaporator 20 described in the first embodiment and the like is omitted, but the present invention is not limited to this and the second device evaporator 20 described in the first embodiment and the like may be provided. This makes it possible to secure a sufficient adjustment range for the distribution between the heat absorption capacity for absorbing heat from the blown air blown into the space to be air-conditioned and the heat absorption capacity for absorbing heat from the heat absorption medium.

[0138] Fifth embodiment Next, a fifth embodiment will be described with reference to Fig. 26. In this embodiment, differences from the first embodiment will be mainly described.

[0139] The heat exchange system 1 of this embodiment is configured such that one of the evaporators 18 for the first equipment and the evaporator 20 for the second equipment, which are arranged in parallel with the refrigerant flow, has a greater heat exchange capacity than the other evaporator.

[0140] 26, the first equipment evaporator 18 is larger in size than the second equipment evaporator 20 so as to increase the heat exchange capacity between the refrigerant and the low-temperature side heat medium. That is, the first equipment evaporator 18 has a larger volume than the second equipment evaporator 20 so as to increase the flow rate of the refrigerant.

[0141] Here, the pressure loss of the refrigerant increases as the flow rate of the refrigerant increases. Also, the pressure loss of the refrigerant increases as the length of the refrigerant path through which the refrigerant flows increases. Taking these factors into consideration, in the heat exchange system 1 of this embodiment, the length La of the refrigerant path from the large first equipment evaporator 18 to the compressor 11 is shorter than the length Lb of the refrigerant path from the small second equipment evaporator 20 to the compressor 11.

[0142] The rest is the same as in the first embodiment. The heat exchange system 1 of the present embodiment can obtain the same effects as in the first embodiment, which are achieved by a configuration common to the first embodiment or an equivalent configuration.

[0143] Moreover, the heat exchange system 1 of this embodiment has the following features.

[0144] (1) Of the first equipment evaporator 18 and the second equipment evaporator 20, one of the evaporators is configured to have a larger heat exchange capacity than the other evaporator. The refrigerant path of the one evaporator to the compressor 11 is shorter than that of the other evaporator. This can reduce the pressure loss of the refrigerant, thereby improving the efficiency of the heat exchange system 1.

[0145] (Modification of the fifth embodiment) In the fifth embodiment, the first equipment evaporator 18 is larger in size than the second equipment evaporator 20, but this is not limiting, and for example, the second equipment evaporator 20 may be larger in size than the first equipment evaporator 18. In this case, the length Lb of the refrigerant path from the second equipment evaporator 20 to the compressor 11 may be configured to be shorter than the length La of the refrigerant path from the first equipment evaporator 18 to the compressor 11.

[0146] (Other embodiments) Representative embodiments of the present disclosure have been described above, but the present disclosure is not limited to the above-described embodiments and can be modified in various ways, for example, as described below.

[0147] In the above embodiment, the refrigeration cycle 10 has been described with a specific configuration, but the refrigeration cycle 10 may have a configuration different from that described above. The refrigeration cycle 10 of the above embodiment includes the liquid receiver 13 and the evaporation pressure control valve 16, but these are not essential and may be omitted. In addition, the number of evaporators that exchange heat between the low-temperature side heat medium and the refrigerant is not limited to two, and may be three or more.

[0148] In the above embodiment, the high temperature side circuit 50 has been described with a specific configuration, but the high temperature side circuit 50 may have a configuration different from that described above. For example, the high temperature side circuit 50 may be configured so that the heat of the high temperature side heat medium can be used to heat the heat generating device 63.

[0149] In the above embodiment, the low temperature side circuit 60 has been described with a specific configuration, but the low temperature side circuit 60 may have a configuration different from that described above.

[0150] The refrigeration cycle 10 of the above embodiment is configured as a receiver cycle in which the liquid receiving part 13 is provided downstream of the condenser 12, but is not limited thereto. The refrigeration cycle 10 may be configured as a cycle in which the liquid receiving part 13 is not provided. The refrigeration cycle 10 may be configured as an accumulator cycle in which an accumulator is provided on the refrigerant suction side of the compressor 11, for example.

[0151] The refrigeration cycle 10 may be configured as a gas injection cycle in which the compressor 11 capable of two-stage compression is employed, pressure reducing valves are provided before and after the liquid receiving section 13, and the gas phase refrigerant separated in the liquid receiving section 13 is returned to the middle stage section of the compressor 11. In the refrigeration cycle 10 configured in this manner, a high-pressure refrigerant may flow in the high-pressure flow passage section 211 of the internal heat exchanger 21, or an intermediate-pressure refrigerant that has been reduced in pressure by a pressure reducing valve disposed upstream of the liquid receiving section 13 may flow.

[0152] In the above-described embodiment, the heat exchange system 1 is applied to an air conditioning system of a vehicle, but the heat exchange system 1 is not limited to air conditioning systems for mobile objects, and can also be applied to, for example, stationary air conditioning systems or portable air conditioning systems.

[0153] In the above-described embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential, except in cases where it is particularly expressly stated that they are essential or where they are clearly considered to be essential in principle.

[0154] In the above-described embodiments, when numerical values ​​such as the number, values, amounts, ranges, etc. of components of the embodiments are mentioned, they are not limited to the specific numbers unless it is specifically stated as required or unless it is clearly limited to a specific number in principle.

[0155] In the above-described embodiments, when referring to the shapes, positional relationships, etc. of components, etc., there is no limitation to those shapes, positional relationships, etc., unless specifically stated or in principle limited to a specific shape, positional relationship, etc.

[0156] The control unit and the method of the present disclosure may be implemented in a special-purpose computer provided by configuring a processor and a memory programmed to execute one or more functions embodied in a computer program. The control unit and the method of the present disclosure may be implemented in a special-purpose computer provided by configuring a processor with one or more dedicated hardware logic circuits. The control unit and the method of the present disclosure may be implemented in one or more special-purpose computers configured by a combination of a processor and a memory programmed to execute one or more functions and a processor configured with one or more hardware logic circuits. The computer program may also be stored in a computer-readable non-transitory tangible recording medium as instructions executed by a computer. [Explanation of symbols]

[0157] 1. Heat exchange system 11 Compressor 12 Condenser (heat radiator) 14 First pressure reducing valve (first pressure reducing section) 15 Air conditioning evaporator (first evaporator) 17 Second pressure reducing valve (second pressure reducing section) 18 Evaporator for first device (second evaporator) 20, 20A Evaporator for second equipment (heat exchanger for heat absorption, third evaporator) 21 Internal heat exchanger (heat exchanger for heat absorption)

Claims

1. 1. A heat exchange system comprising: A compressor (11) that compresses and discharges a refrigerant; a radiator (12) that radiates heat by exchanging heat between the refrigerant discharged from the compressor and a heat radiating medium that radiates heat to at least one of an external space and an air-conditioned space; a first pressure reducing section (14) for reducing the pressure of the refrigerant that has passed through the radiator; a second pressure reducing section (17) arranged in parallel with the first pressure reducing section downstream of the radiator and reducing the pressure of the refrigerant that has passed through the radiator; a first evaporator (15) that evaporates the refrigerant decompressed in the first decompression section by heat exchange with air to be blown into the space to be air-conditioned; a second evaporator (18) that evaporates the refrigerant decompressed in the second decompression section by heat exchange with a heat absorbing medium that absorbs heat from at least one of a heat generating device (63) and the external space; a heat absorbing heat exchanger (20, 20A, 21) for adjusting the amount of heat absorbed from the heat absorbing medium by heat exchange between the refrigerant and a predetermined fluid; a capacity adjustment unit (100a) that adjusts the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the heat absorption medium by changing the heat exchange amount in one of the second evaporator and the heat absorption heat exchanger.

2. a third pressure reducing section (19) arranged in parallel with the first pressure reducing section and the second pressure reducing section downstream of the radiator, and reducing the pressure of the refrigerant that has passed through the radiator; The heat absorption heat exchanger is a third evaporator that evaporates the refrigerant decompressed in the third decompression unit by heat exchange with the heat absorption medium, The heat exchange system of claim 1, wherein the capacity adjustment unit adjusts the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the heat absorption medium by increasing the amount of the refrigerant supplied to the third evaporator or decreasing the amount of the refrigerant supplied to the third evaporator.

3. When a scene in which cooling of the air-conditioned space is prioritized is defined as a first scene, and a scene in which heat absorption from the heat-generating device or the external space is prioritized is defined as a second scene, 3. The heat exchange system of claim 2, wherein the capacity adjustment unit increases the amount of refrigerant supplied to the third evaporator when the second scene occurs, thereby increasing the amount of heat exchange between the refrigerant and the heat absorption medium, and reduces the amount of refrigerant supplied to the third evaporator when the first scene occurs, thereby increasing the amount of heat exchange between the refrigerant and the blown air.

4. A heat absorption circuit (60) through which the heat absorption medium flows, In the heat absorption circuit, the second evaporator and the third evaporator are connected in parallel so that the heat absorption medium is distributed to the second evaporator and the third evaporator.

4. The heat exchange system according to claim 3, wherein the capacity adjustment unit increases the amount of the heat absorption medium supplied to the third evaporator when the second scene occurs to increase the amount of heat exchange between the refrigerant and the heat absorption medium, and reduces the amount of the heat absorption medium supplied to the third evaporator when the first scene occurs.

5. A heat absorption circuit (60) through which the heat absorption medium flows, The heat exchange system according to claim 3 , wherein the second evaporator and the third evaporator are connected in series in the heat absorption circuit such that the heat absorption medium flows from one of the second evaporator and the third evaporator to the other.

6. The heat absorption heat exchanger is a third evaporator that evaporates the refrigerant that has passed through the first evaporator by heat exchange with the heat absorption medium, The heat exchange system of claim 1, wherein the capacity adjustment unit adjusts the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the heat absorption medium by increasing the amount of the refrigerant supplied to the second evaporator or decreasing the amount of the refrigerant supplied to the second evaporator.

7. When a scene in which cooling of the air-conditioned space is prioritized is defined as a first scene, and a scene in which heat absorption from the heat-generating device or the external space is prioritized is defined as a second scene, The capacity adjustment unit is When the second scene occurs, the refrigerant is supplied to both the second evaporator and the third evaporator to increase the amount of heat exchanged between the refrigerant and the heat absorbing medium; The heat exchange system according to claim 6, wherein when the first scene occurs, the amount of heat exchange between the refrigerant and the blown air is increased by reducing the supply of the refrigerant to the second evaporator while supplying the refrigerant to the third evaporator.

8. The heat absorption heat exchanger is a third evaporator (20A) that evaporates the refrigerant that has passed through the first evaporator by heat exchange with the heat absorption medium, The heat exchange system of claim 1, wherein the capacity adjustment unit adjusts the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the heat absorption medium by increasing the amount of the heat absorption medium supplied to the third evaporator or decreasing the amount of the heat absorption medium supplied to the third evaporator.

9. When a scene in which cooling of the air-conditioned space is prioritized is defined as a first scene, and a scene in which heat absorption from the heat-generating device or the external space is prioritized is defined as a second scene, The capacity adjustment unit is When the second scene occurs, the heat absorbing medium is supplied to both the second evaporator and the third evaporator to increase the amount of heat exchange between the refrigerant and the heat absorbing medium; 9. The heat exchange system according to claim 8, wherein when the first scene occurs, the heat absorption medium is supplied to the second evaporator while the amount of the heat absorption medium supplied to the third evaporator is reduced to increase the amount of heat exchange between the refrigerant and the blown air.

10. 10. The heat exchange system according to claim 6, further comprising a pressure regulating valve (16) provided between the first evaporator and the third evaporator for regulating the pressure of the refrigerant passing through the first evaporator.

11. The heat absorption heat exchanger is an internal heat exchanger (21) that exchanges heat between the refrigerant before being decompressed in the second decompression section and the refrigerant after being decompressed in the first decompression section, The heat exchange system according to claim 1 , wherein the capacity adjustment unit adjusts the distribution of the heat absorption capacity to absorb heat from the blown air and the heat absorption capacity to absorb heat from the heat absorption medium by changing the opening area of ​​the second pressure reduction unit.

12. When a scene in which cooling of the air-conditioned space is prioritized is defined as a first scene, and a scene in which heat absorption from the heat-generating device or the external space is prioritized is defined as a second scene, The capacity adjustment unit is When the first stage is reached, an opening area of ​​the second pressure reducing section is reduced to increase a flow rate of the refrigerant flowing through the first evaporator and reduce a heat exchange amount of the internal heat exchanger, The heat exchange system according to claim 11, wherein when the second scene occurs, an opening area of ​​the second pressure reducing section is increased to increase a flow rate of the refrigerant flowing through the second evaporator and to increase a heat exchange amount of the internal heat exchanger.

13. 5. A heat exchange system according to claim 2, wherein one of the second evaporator and the third evaporator is larger in size than the other evaporator so as to have a larger heat exchange capacity, and the refrigerant path to the compressor is shorter than that of the other evaporator.

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