WO2021015270A1 - Heat management apparatus - Google Patents

Abstract

This heat management apparatus comprises: a first heat dissipation unit (12) that dissipates heat from the refrigerant discharged from a compressor; a second heat dissipation unit (16A) that dissipates heat from the refrigerant discharged from the first heat dissipation unit into an air flow; an evaporator (20) that evaporates the refrigerant; a chiller (24) that evaporates the refrigerant by causing the refrigerant to absorb heat from a heat medium; a bypass refrigerant passage (18) that allows the refrigerant discharged from the first heat dissipation unit to flow through the evaporator and chiller, bypassing the second heat dissipation unit; a switching valve (14) that sets the bypass refrigerant passage to a first state in which the bypass refrigerant passage is closed or a second state in which the bypass refrigerant passage is open; a radiator (16B) that performs heat exchange between the heat medium and the air flow; and a heat medium circuit (53) that circulates the heat medium between the chiller and the radiator. In a first mode in the first state, the refrigerant in the second heat dissipation unit dissipates heat into the air flow through the radiator. In a second mode in which the heat medium in the heat medium circuit is circulating in the second state, the heat medium in the radiator absorbs heat from the air flow through the second heat dissipation unit.

Description

Thermal management device Cross-reference to related applications

This application is based on Japanese Patent Application No. 2019-136355 filed on July 24, 2019, the contents of which are incorporated herein by reference.

This disclosure relates to a heat management device.

Conventionally, a heat pump system includes a compressor, an indoor condenser, a first expansion valve, a second expansion valve, an outdoor unit, an indoor evaporator, and a switching valve (see, for example, Patent Document 1). At the time of heating, the refrigerant discharged from the compressor flows in the order of the indoor condenser → the first expansion valve → the outdoor unit → the compressor. At the time of cooling, the refrigerant discharged from the compressor flows in the order of the outdoor unit → the second expansion valve → the indoor evaporator → the compressor. The switching valve switches between the refrigerant circuit in the heating mode and the refrigerant circuit in the cooling mode. In such a heat pump system, during heating, the outdoor unit functions as an evaporator in which the refrigerant absorbs heat from the outside air and evaporates the refrigerant. During cooling, the outdoor unit functions as a radiator that dissipates heat from the refrigerant to the outside air and condenses the refrigerant.

The outdoor unit has a condensing part that dissipates heat from the refrigerant to the outside air to condense the refrigerant, and the gas-liquid two-phase refrigerant that has passed through the condensing part is separated into a liquid-phase refrigerant and a gas-phase refrigerant, and the liquid phase is stored while storing the gas-phase refrigerant. It is provided with a gas-liquid separation unit that discharges the refrigerant.

The outdoor unit is provided with a supercooling unit that dissipates heat from the liquid phase refrigerant discharged from the gas-liquid separation unit to the outside air to supercool the liquid phase refrigerant. As a result, the heat exchange efficiency during cooling can be improved by setting an appropriate degree of supercooling in the refrigeration cycle.

Japanese Unexamined Patent Publication No. 2014-113975

According to the study of the present inventor, in the above heat pump system, in order to improve the heat exchange efficiency during cooling, the cross-sectional area of the refrigerant flow path of the supercooling part is set rather than the cross-sectional area of the refrigerant flow path of the condensing part. It is desirable to make it smaller.

However, during heating, a gas-liquid two-phase refrigerant with a dryness close to 100% flows through the refrigerant flow path having a small cross-sectional area in the supercooled portion. Therefore, there is a possibility that the pressure loss generated when the refrigerant passes through the supercooled portion becomes significantly large. Therefore, when the outdoor unit functions as an evaporator during heating, the heat exchange efficiency between the outside air and the refrigerant in the supercooling unit decreases.

In view of the above points, the present disclosure aims to provide a heat management device that improves heat exchange efficiency.

According to one aspect of the present disclosure, the heat management device includes a compressor that sucks in and compresses and discharges the refrigerant.
The first radiator that dissipates heat from the refrigerant discharged from the compressor,
A second radiator that dissipates heat from the refrigerant that has passed through the first radiator to the air flow,
A first pressure reducing valve and a second pressure reducing valve for reducing the pressure of the refrigerant that has passed through the first radiator,
An evaporator that evaporates the refrigerant that has passed through the first pressure reducing valve,
A chiller that evaporates the refrigerant that has passed through the second pressure reducing valve by absorbing heat from the heat medium.
A bypass refrigerant passage that allows the refrigerant that has passed through the first radiator to bypass the second radiator and flow to the first pressure reducing valve and the second pressure reducing valve.
Between the first state in which the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator are opened and the bypass refrigerant passage is closed, and the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator. A switching valve that is set to one of the second states in which the bypass refrigerant passage is opened and the bypass refrigerant passage is opened.
A radiator that exchanges heat between the heat medium and the air flow,
A heat carrier circuit for circulating the heat medium between the chiller and the radiator.
In the first mode in which the switching valve is set to the first state, the refrigerant in the second radiator dissipates heat to the air flow via the radiator.
In the second mode in which the heat medium in the heat medium circuit circulates with the switching valve set to the second state, the heat medium in the radiator absorbs heat from the air flow via the second radiator.

As a result, in the first mode, the refrigerant in the second radiator dissipates heat to the air via the connection portion and the radiator. Therefore, the refrigerant can dissipate heat to the air from the second radiator and the radiator. Therefore, the heat exchange efficiency between the refrigerant and the air flow can be improved by using only the second radiator of the radiator and the second radiator as compared with the case where the refrigerant dissipates heat to the air.

In the second mode, the radiator absorbs heat from the air through the second radiator. Therefore, the heat medium can absorb heat from the air via the radiator and the second radiator. Therefore, the radiator alone of the radiator and the second radiator can improve the heat exchange efficiency between the heat medium and the air flow as compared with the case where the heat medium absorbs heat from the air flow.

From the above, it is possible to provide a heat management device that improves heat exchange efficiency. The reference numerals in parentheses attached to each component or the like indicate an example of the correspondence between the component or the like and the specific component or the like described in the embodiment described later.

It is a figure which shows the whole structure of the refrigerating cycle and the cooling water circuit of the vehicle-mounted heat management apparatus in 1st Embodiment. FIG. 1 is a partially enlarged view for showing the arrangement relationship of a secondary battery, a cooler, and an electric heater in the battery unit in FIG. It is a figure which shows the arrangement relation of the heat exchange core and each tank of the air / refrigerant heat exchanger of the outdoor unit in FIG. 1, and the flow direction of a refrigerant. It is a figure which shows the arrangement relation of the heat exchange core and each tank of the air / cooling water heat exchanger of the outdoor unit in FIG. 1, and the flow direction of a refrigerant. It is a perspective view which shows the plurality of refrigerant tubes and a plurality of heat exchange fins constituting the air / cooling water heat exchanger and the air / refrigerant heat exchanger in FIG. 1. It is a figure which shows the refrigerant flow of the refrigerating cycle in the cooling mode of 1st Embodiment, and the flow of cooling water of a cooling water circuit. It is a figure which shows the refrigerant flow of the refrigerating cycle in the heating mode of 1st Embodiment, and the flow of cooling water of a cooling water circuit. It is a figure which shows the refrigerant flow of the refrigerating cycle in the heater mode of 1st Embodiment, and the flow of cooling water of a cooling water circuit. It is a figure which shows the refrigerant flow of the refrigerating cycle in the defrosting mode of 1st Embodiment, and the flow of cooling water of a cooling water circuit. It is a figure which shows the whole structure of the refrigerating cycle and the cooling water circuit of the vehicle-mounted heat management apparatus in 2nd Embodiment. It is a figure which shows the whole structure of the refrigerating cycle and the cooling water circuit of the vehicle-mounted heat management apparatus in 3rd Embodiment. It is a figure which shows the whole structure of the refrigerating cycle and the cooling water circuit of the vehicle-mounted heat management apparatus in 4th Embodiment. It is a figure which shows the whole structure of the refrigerating cycle and the cooling water circuit of the vehicle-mounted heat management apparatus in 5th Embodiment, and is the figure which shows the refrigerant flow of the refrigerating cycle in the defrosting mode, and the cooling water flow of a cooling water circuit. ..

Hereinafter, embodiments of the present disclosure will be described with reference to the figures. In the following embodiments, the parts that are the same or equal to each other are designated by the same reference numerals in the drawings in order to simplify the description.

(First Embodiment)
FIG. 1 shows the configuration of the vehicle-mounted heat management device 1 of the first embodiment.

As shown in FIG. 1, the vehicle-mounted heat management device 1 of the present embodiment includes a compressor 10, an indoor condenser 12, a three-way valve 14, an outdoor unit 16, a bypass refrigerant passage 18, expansion valves 20a and 20b, an evaporator 20, and a chiller 24. , The accumulator 26, and the pressure regulating valve 28.

The vehicle-mounted heat management device 1 of the present embodiment includes pumps 36a, 36b, on-off valves 38a, 38b, 38c, 38d, a three-way valve 40, an electric heater 42, a battery unit 44, a motor generator 46, and an inverter 48.

The compressor 10 sucks in the refrigerant, compresses it, and discharges it. The compressor 10 of the present embodiment is an electric compressor including a compression mechanism and an electric motor for driving the compression mechanism.

The indoor condenser 12 is a first radiator that dissipates heat from the high-pressure refrigerant to the air flow by heat exchange between the high-pressure refrigerant discharged from the compressor 10 and the air flow. The indoor condenser 12 is arranged in the indoor air conditioning casing 2.

The indoor air conditioner casing 2 constitutes an indoor air conditioner that air-conditions the vehicle interior together with an indoor condenser 12, an evaporator 20, an air mix door 5, a blower 4, and the like. Although an axial fan is shown as the blower 4 in FIG. 1 and the like, in reality, for example, a centrifugal fan is used.

The indoor air-conditioning casing 2 is arranged inside the instrument panel on the front side in the vehicle traveling direction in the vehicle interior. The blower 4 generates an air flow toward the vehicle interior in the indoor air-conditioning casing 2.

The air mix door 5 adjusts the ratio of the amount of cold air blown from the evaporator 20 in the indoor air conditioning casing 2 to the amount of air passing through the indoor condenser 12 and the amount of air passing through the bypass passage 3.

As the air mix door 5, various doors such as a film door, a sliding door, a plate door, and a rotary door can be used. FIG. 1 and the like show a film door as the air mix door 5.

The bypass passage 3 is a bypass passage in which the cold air from the evaporator 20 of the indoor air-conditioning casing 2 bypasses the indoor condenser 12 and flows toward the vehicle interior.

The three-way valve 14 connects the refrigerant inlets of the expansion valves 20a and 20b and the refrigerant inlet of the air / refrigerant heat exchanger 16A to the refrigerant outlet of the indoor condenser 12, and the other refrigerant. A valve body that closes between the inlet and the refrigerant outlet of the indoor condenser 12 is provided.

Here, the other refrigerant inlet refers to the respective refrigerant inlets of the expansion valves 20a and 20b, and the remaining refrigerant inlets other than one of the refrigerant inlets of the air / refrigerant heat exchanger 16A of the outdoor unit 16. Is.

The three-way valve 14 of the present embodiment is a switching valve that is set to either the first state or the second state as described later. The first state is a state in which the refrigerant outlet of the indoor condenser 12 and the refrigerant inlet of the air / refrigerant heat exchanger 16A are opened and the bypass passage 3 is opened.

The second state is a state in which the space between the refrigerant outlet of the indoor condenser 12 and the refrigerant inlet of the air / refrigerant heat exchanger 16A is closed, and the bypass passage 3 is closed. The valve body of the three-way valve 14 is driven by an electric actuator. The electric actuator is controlled by the electronic control device 32. In FIG. 1, the electronic control unit 32 is referred to as an ECU.

The three-way valve 14 has a refrigerant inlet connected to the refrigerant outlet of the indoor condenser 12, a first refrigerant outlet connected to the refrigerant inlet of the air / refrigerant heat exchanger 16A, and the refrigerants of the expansion valves 20a and 20b, respectively. It is provided with a second refrigerant outlet connected to the inlet.

The outdoor unit 16 is a first radiator arranged in the engine room of the vehicle. The engine room is a storage room that is arranged on the front side in the vehicle traveling direction with respect to the vehicle room and stores a traveling drive source such as an electric motor and an engine.

As a result, the outdoor unit 16 is arranged outside the vehicle interior (that is, outdoors) of the vehicle.

Specifically, the outdoor unit 16 includes an air / refrigerant heat exchanger 16A and an air / cooling water heat exchanger 16B. The air / refrigerant heat exchanger 16A is a second radiator that dissipates heat from the refrigerant to the air flow by heat exchange between the refrigerant flowing from the indoor condenser 12 through the three-way valve 14 and the air flow blown by the blower 16C. ..

The air / cooling water heat exchanger 16B is a radiator that exchanges heat between the cooling water and the air flow blown by the blower 16C, as will be described later. Cooling water is a heat medium used to transfer heat as described below. The air / cooling water heat exchanger 16B includes cooling water inlets and outlets 160 and 161 for entering or discharging cooling water.

In this embodiment, as will be described later, the flow direction of the cooling water flowing through the air / cooling water heat exchanger 16B changes depending on the air conditioning mode. The air / cooling water heat exchanger 16B is arranged on the front side in the vehicle traveling direction with respect to the air / refrigerant heat exchanger 16A.

The air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B are thermally connected to each other. The specific structure of the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B will be described later.

The blower 16C is arranged in the engine room on the rear side in the vehicle traveling direction with respect to the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B. The blower 16C is an electric fan for generating an air flow (that is, an outside air flow) passing through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

The air / cooling water heat exchanger 16B is arranged on the upstream side in the air flow direction with respect to the air / refrigerant heat exchanger 16A. The blower 16C is controlled by the electronic control device 32. The bypass refrigerant passage 18 is connected between the second refrigerant outlet of the three-way valve 14 and the respective refrigerant inlets of the expansion valves 20a and 20b. As described above, the second refrigerant outlet is the refrigerant outlet connected to the respective refrigerant inlets of the expansion valves 20a and 20b in the three-way valve 14.

The bypass refrigerant passage 18 is a refrigerant passage that allows the refrigerant flowing from the indoor condenser 12 through the three-way valve 14 to bypass the air / refrigerant heat exchanger 16A of the outdoor unit 16 and flow to the respective refrigerant inlets of the expansion valves 20a and 20b.

The expansion valve 20a is the flow path cross-sectional area (that is, the throttle opening) of the refrigerant passage between the bypass refrigerant passage 18 and the common connection portion 19 of the refrigerant outlet of the air / refrigerant heat exchanger 16A and the refrigerant inlet of the evaporator 20. A valve body for adjusting the valve body and an electric actuator for driving the valve body are provided. The valve body is controlled by the electronic control device 32 via an electric actuator. The expansion valve 20a is a first pressure reducing valve for reducing the pressure of the refrigerant flowing from the bypass refrigerant passage 18 or the air / refrigerant heat exchanger 16A to the refrigerant inlet of the evaporator 20.

The evaporator 20 is an evaporator arranged on the upstream side in the air flow direction with respect to the indoor condenser 12 in the indoor air conditioning casing 2. The evaporator 20 is a heat exchanger that exchanges heat between the refrigerant passing through the expansion valve 20a and the air flow, absorbs heat from the air flow, and evaporates the refrigerant.

The expansion valve 20b is the flow path cross-sectional area (that is, throttle opening) of the refrigerant passage between the bypass refrigerant passage 18 and the common connection portion 19 of the refrigerant outlet of the air / refrigerant heat exchanger 16A and the refrigerant inlet of the chiller 24. A valve body for adjusting the valve body and an electric actuator for driving the valve body are provided.

The valve body is controlled by the electronic control device 32 via an electric actuator. The expansion valve 20b is a second pressure reducing valve for reducing the pressure of the refrigerant flowing from the bypass refrigerant passage 18 or the air / refrigerant heat exchanger 16A to the refrigerant inlet of the chiller 24.

The expansion valves 20a and 20b are arranged in parallel with respect to the refrigerant flow direction between the bypass refrigerant passage 18 and the common connection portion 19 of the refrigerant outlet of the air / refrigerant heat exchanger 16A and the refrigerant inlet of the compressor 10. The chiller 24 is a water / refrigerant heat exchanger that exchanges heat between the refrigerant that has passed through the expansion valve 20b and the cooling water, and the refrigerant absorbs heat from the cooling water.

The accumulator 26 separates the gas-liquid two-phase refrigerant that has passed through the chiller 24 or the evaporator 20 into a liquid phase refrigerant and a gas phase refrigerant, stores the liquid phase refrigerant, and guides the gas phase refrigerant to the refrigerant inlet of the compressor 10. It is a gas-liquid separator. The pressure regulating valve 28 plays a role of bringing the refrigerant pressure in the evaporator 20 closer to a predetermined pressure in order to bring the refrigerant temperature in the evaporator 20 closer to a predetermined temperature.

The electronic control device 32 controls the compressor 10, expansion valves 20a, 20b, etc. using the output signals of the pressure sensors 30a, 30b, etc. The pressure sensor 30a is a pressure sensor that detects the pressure of the high-pressure refrigerant that has passed through the indoor condenser 12. The pressure sensor 30b is a pressure sensor that detects the pressure of the low-pressure refrigerant that has passed through the chiller 24.

The chiller 24, together with the pump 36a and the battery unit 44, constitutes cooling water circuits 50, 53, and the like. The pump 36a is a second pump that circulates the cooling water in the cooling water circuit 50.

The cooling water circuit 50 is a cooling water circuit for circulating the cooling water from the pump 36a in the order of the chiller 24 → the battery unit 44 → the pump 36a.

That is, the cooling water circuit 50 is a third heat medium circuit for circulating cooling water between the chiller 24 and the electric heater 42. The pump 36a is an electric pump controlled by the electronic control device 32.

As shown in FIG. 2, the battery unit 44 includes a secondary battery 44a and a heat exchanger 44b. The secondary battery 44a stores DC power for supplying power to the motor generator 46. The secondary battery 44a also functions as a heat receiving unit that receives heat from the cooling water. In FIG. 1 and the like, the battery unit 44 is referred to as “Batt”.

The heat exchanger 44b is a heat exchanger that exchanges heat between the secondary battery 44a and the cooling water. The heat exchanger 44b is provided with cooling water inlets and outlets 70 and 71 for entering or discharging the cooling water. The direction of flow through the heat exchanger 44b changes depending on the operation, as will be described later.

The electric heater 42 is arranged in the heat exchanger 44b. The electric heater 42 is a second heating element that heats the cooling water flowing through the heat exchanger 44b. The electric heater 42 is controlled by the electronic control device 32. In addition, in FIG. 1 and the like, the electric heater 42 is referred to as "EHTR".

The on-off valve 38b includes a valve body that opens and closes between the cooling water outlet of the chiller 24 and the cooling water inlet / outlet 71 of the heat exchanger 44b of the battery unit 44, and an electric actuator that drives the valve body. The valve body is controlled by the electronic control device 32 via an electric actuator.

The on-off valve 38d includes a valve body that opens and closes between the cooling water inlet of the pump 36a and the cooling water inlet / outlet 70 of the heat exchanger 44b of the battery unit 44, and an electric actuator that drives the valve body.

The pump 36b is the first pump that constitutes the cooling water circuit 51 together with the battery unit 44, the motor generator 46, and the inverter 48.

The pump 36b circulates the cooling water in the cooling water circuit 51. The cooling water circuit 51 is a second heat medium circuit for circulating the cooling water from the pump 36b in the order of the heat exchanger 44b of the battery unit 44 → the cooler 48a of the inverter 48 → the cooler 46a of the motor generator 46 → the pump 36b. Is.

The inverter 48 is a first heating element including a cooler 48a as a heat exchanger that dissipates heat from a plurality of semiconductor elements constituting the inverter 48 to cooling water. In addition, in FIG. 1 and the like, the inverter 48 is referred to as “INV”.

The motor generator 46 is a first heating element including a traveling electric motor for driving the driving wheels of the vehicle and a cooler 46a. The traveling electric motor also functions as a generator that generates electricity by rotating the drive wheels of the vehicle. The cooler 46a is a heat exchanger that dissipates heat from the traveling electric motor to the cooling water. The pump 36b is controlled by the electronic control device 32.

The chiller 24 constitutes a cooling water circuit 53 together with the pump 36a and the air / cooling water heat exchanger 16B. The pump 36a circulates the cooling water in the cooling water circuit 53. The cooling water circuit 53 is a first heat medium circuit for circulating the cooling water from the pump 36a in the order of the chiller 24 → on-off valve 38a → air / cooling water heat exchanger 16B → on-off valve 38c → pump 36a.

The three-way valve 40 opens between one of the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B and the cooling water inlet / outlet 70 of the heat exchanger 44b of the battery unit 44 and the cooling water outlet of the pump 36b.

The three-way valve 40 closes between the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B and the cooling water inlet / outlet 70 of the heat exchanger 44b of the battery unit 44, and the other and the cooling water outlet of the pump 36b. The three-way valve 40 is controlled by the electronic control device 32.

The on-off valve 38a includes a valve body that opens and closes between the cooling water outlet of the chiller 24 and the cooling water inlet / outlet 161 of the air / cooling water heat exchanger 16B, and an electric actuator for driving the valve body.

The on-off valve 38c includes a valve body that opens and closes between the cooling water inlet of the pump 36a and the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B, and an electric actuator that drives the valve body. The on-off valves 38a and 38c are controlled by the electronic control device 32.

The cooling water circuits 50, 51, and 52 configured in this way are provided with cooling water temperature sensors 50a, 50b, and 50c.

The cooling water temperature sensor 50a is a temperature sensor that detects the temperature of the cooling water flowing out of the chiller 24. The cooling water temperature sensor 50b is a temperature sensor that detects the temperature of the cooling water flowing into the cooler 48a of the inverter 48.

The cooling water temperature sensor 50c is a temperature sensor that detects the temperature of the cooling water flowing out from the heat exchanger 44b of the battery unit 44. The detection signals of the cooling water temperature sensors 50a, 50b, 50c are used when the electronic control device 32 controls the on-off valves 38a, 38b, 38c, 38d and the like.

Next, the specific structures of the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B of the present embodiment will be described with reference to FIGS. 3, 4, and 5.

FIGS. 3, 4 and 5 show an example in which XYZ coordinates are set for convenience of explanation. The X, Y, and Z directions in the XYZ coordinates are directions orthogonal to each other.

As shown in FIG. 3, the air / refrigerant heat exchanger 16A includes a condensing unit 100, a supercooling unit 110, and a gas-liquid separation unit 120. The condensing unit 100 includes tanks 101a, 101b, 101c, 101d, and heat exchange path units 102a, 102b, 102c.

The tanks 101a and 101b are arranged on one side in the X direction with respect to the heat exchange path portions 102a, 102b and 102c. The tanks 101c and 101d are arranged on the opposite side in the X direction with respect to the heat exchange path portions 102a, 102b and 102c.

The heat exchange path portion 102a includes a plurality of refrigerant tubes 130a extending in the X direction. The heat exchange path portion 102b includes a plurality of refrigerant tubes 130a extending in the X direction. The heat exchange path portion 102c includes a plurality of refrigerant tubes 130a extending in the X direction.

The plurality of refrigerant tubes 130a in the heat exchange path portions 102a, 102b, 102c are arranged in the Z direction. The heat exchange path portion 102a is arranged on one side in the Z direction with respect to the heat exchange path portion 102b. The heat exchange path portion 102b is arranged on one side in the Z direction with respect to the heat exchange path portion 102c.

The tank 101a distributes the refrigerant to the plurality of refrigerant tubes 130a of the heat exchange path portion 102a. The tank 101c collects the refrigerant that has passed through the plurality of refrigerant tubes 130a of the heat exchange path portion 102a and distributes the refrigerant to the plurality of refrigerant tubes 130a of the heat exchange path portion 102b.

The tank 101b collects the refrigerant that has passed through the plurality of refrigerant tubes 130a of the heat exchange path portion 102b and distributes the refrigerant to the plurality of refrigerant tubes 130a of the heat exchange path portion 102c. The tank 101d collects the refrigerant that has passed through the plurality of refrigerant tubes 130a of the heat exchange path portion 102c and guides the refrigerant to the gas-liquid separation portion 120.

The gas-liquid separation unit 120 plays a role of separating the refrigerant from the tank 101d into a gas phase refrigerant and a liquid phase refrigerant, storing the vapor phase refrigerant, and guiding the liquid phase refrigerant to the tank 111b of the supercooling unit 110. The supercooling unit 110 is arranged on the opposite side in the Z direction with respect to the condensing unit 100. The supercooling unit 110 includes tanks 111a and 111b and a heat exchange path unit 111c.

The tank 111a is arranged on the other side in the Z direction with respect to the tank 101b. The tank 111b is arranged on the opposite side of the tank 101d in the Z direction. The tank 111b distributes the liquid phase refrigerant from the gas-liquid separation unit 120 to the plurality of refrigerant tubes 130a of the heat exchange path unit 111c.

The tank 111a plays a role of recovering the liquid phase refrigerant that has passed through the plurality of refrigerant tubes 130a of the heat exchange path portion 111c and guiding them to the expansion valves 20a and 20b. The flow path cross-sectional area of the plurality of refrigerant tubes 130a of the supercooling section 110 of the present embodiment is smaller than the flow path cross-sectional area of the plurality of refrigerant tubes 130a of the condensing section 100.

The heat exchange path portions 102a, 102b, 102c, and 111c of the present embodiment each form a heat exchange core 140 together with a plurality of heat exchange fins 135a. The plurality of heat exchange fins 135a form a plurality of air flow paths through which an air flow flows in the Y direction.

As shown in FIG. 4, the air / cooling water heat exchanger 16B includes tanks 120a and 120b, and a heat exchange core 120c.

The heat exchange core 120c includes a plurality of cooling water tubes 130b extending in the X direction and a plurality of heat exchange fins 135b. The plurality of cooling water tubes 130b are arranged in the Z direction. The plurality of heat exchange fins 135b form a plurality of air flow paths through which an air flow flows in the Y direction.

The tank 120a is arranged on one side in the X direction with respect to the heat exchange core 120c. The tank 120a distributes the cooling water to the plurality of cooling water tubes 130b of the heat exchange core 120c. The tank 120b is arranged on one side in the X direction with respect to the heat exchange core 120c. The tank 120b collects the cooling water that has passed through the plurality of cooling water tubes 130b of the heat exchange core 120c.

FIG. 5 shows the arrangement relationship of the refrigerant tube 130a, the cooling water tube 130b, and the heat exchange fins 135a and 135b of the present embodiment.

Heat exchange fins 135a are arranged between two adjacent refrigerant tubes 130a among the plurality of refrigerant tubes 130a. Heat exchange fins 135b are arranged between two adjacent cooling water tubes 130b among the plurality of cooling water tubes 130b.

Each of the plurality of refrigerant tubes 130a is arranged on one side in the Y direction with respect to one of the plurality of cooling water tubes 130b corresponding to the cooling water tube 130b. Each of the heat exchange fins 135a is arranged on one side in the Y direction with respect to one of the plurality of heat exchange fins 135b corresponding to the heat exchange fin 135b.

Each of the heat exchange fins 135a of the present embodiment is connected to one of the plurality of heat exchange fins 135b corresponding to the heat exchange fin 135b via a connecting portion 135c. That is, the heat exchange fins 135a and the heat exchange fins 135b are connected by the connecting portion 135c. The connection portion 135c forms an air flow path between the heat exchange fins 135a and the heat exchange fins 135b through which the air flow generated by the blower 16C passes.

Here, the heat exchange fins 135a and 135b, the cooling water tube 130b, the plurality of connecting portions 135c, and the plurality of refrigerant tubes 130a are made of a metal material such as aluminum.

Next, in the in-vehicle heat management device 1 of the present embodiment, the operation of each air conditioning mode will be described separately with reference to FIGS. 6 to 9. As each air conditioning mode, a cooling mode, a heating mode, a heater mode, and a defrosting mode are used.

(Cooling mode)
First, the cooling mode will be described with reference to FIG. In the cooling mode (that is, the first mode), the electronic control device 32 closes the on-off valves 38a and 38c, respectively, and opens the on-off valves 38b and 38d, respectively.

In addition to this, the electronic control device 32 controls the expansion valve 20a to adjust the flow path cross-sectional area of the refrigerant passage between the refrigerant outlet of the air / refrigerant heat exchanger 16A and the refrigerant inlet of the evaporator 20. The electronic control device 32 controls the expansion valve 20b to adjust the flow path cross-sectional area of the refrigerant passage between the refrigerant outlet of the air / refrigerant heat exchanger 16A and the refrigerant inlet of the chiller 24.

The electronic control device 32 controls the three-way valve 14 to open the space between the refrigerant outlet of the air / refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12, and close the bypass refrigerant passage 18. The electronic control device 32 controls the blower 16C to generate an air flow passing through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

Further, the electronic control device 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Along with this, the high-pressure refrigerant discharged from the compressor 10 passes through the indoor condenser 12.

In this case, the air mix door 5 closes the air inlet of the indoor condenser 12 and opens the bypass passage 3. Therefore, the cold air from the evaporator 20 passes through the bypass passage 3 and is blown into the vehicle interior.

The high-pressure refrigerant that has passed through the indoor condenser 12 flows to the air / refrigerant heat exchanger 16A through the three-way valve 14. At this time, in the air / refrigerant heat exchanger 16A, the high-pressure refrigerant dissipates heat to the air flow blown by the blower 16C.

A part of the high-pressure refrigerant that has passed through the air / refrigerant heat exchanger 16A is depressurized by the expansion valve 20a. The refrigerant decompressed by the expansion valve 20a flows to the evaporator 20. In the evaporator 20, the refrigerant is sucked from the air flow blown from the blower 4 and evaporated.

The pressure of this evaporated refrigerant is adjusted by the pressure regulating valve 28. The pressure-adjusted refrigerant flows through the accumulator 26.

On the other hand, of the high-pressure refrigerant that has passed through the air / refrigerant heat exchanger 16A, the remaining refrigerant other than the refrigerant that flows through the expansion valve 20a flows through the expansion valve 20b. The flowing refrigerant is depressurized by the expansion valve 20b.

The refrigerant decompressed by the expansion valve 20b flows to the chiller 24. In this chiller 24, the refrigerant is sucked from the cooling water and evaporated. This evaporated refrigerant flows to the accumulator 26. The refrigerant flowing through the accumulator 26 is separated into a liquid phase refrigerant and a gas phase refrigerant, and the vapor phase refrigerant flows into the refrigerant inlet of the compressor 10.

In this way, the refrigerant flows in the order of compressor 10 → indoor condenser 12 → three-way valve 14 → air / refrigerant heat exchanger 16A → expansion valve 20a → evaporator 20 → pressure regulating valve 28 → accumulator 26 → compressor 10.

In addition to this, the refrigerant from the air / refrigerant heat exchanger 16A flows in the order of expansion valve 20b → chiller 24 → accumulator 26.

Further, in the cooling water circuit 50, the cooling water flowing from the pump 36a flows to the chiller 24. In this chiller 24, the refrigerant absorbs heat from the cooling water. After the absorbed cooling water passes through the on-off valve 38b, it flows to the cooling water inlet / outlet 71 of the heat exchanger 44b of the battery unit 44.

The electronic control device 32 stops the electric heater 42. In this case, in the heat exchanger 44b, the cooling water receives the heat released from the secondary battery 44a. The cooling water radiated from the secondary battery 44a flows into the pump 36a through the on-off valve 38d.

Therefore, the cooling water flows in the order of pump 36a → chiller 24 → on-off valve 38b → heat exchanger 44b → on-off valve 38d → pump 36a. That is, cooling water is circulated between the chiller 24 and the heat exchanger 44b. Therefore, in the chiller 24, the heat generated from the secondary battery 44a is released to the refrigerant.

The electronic control device 32 controls the three-way valve 40 to open a space between the cooling water outlet of the pump 36b and the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B, and opens the cooling water outlet of the pump 36b and the battery unit. Close the space between the heat exchanger 44b 44 and the cooling water inlet / outlet 70.

Therefore, in the cooling water circuit 52, the cooling water flowing from the pump 36b flows through the three-way valve 40 to the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B. In this air / cooling water heat exchanger 16B, when the cooling water flows through the plurality of cooling water tubes 130b, the cooling water in the plurality of cooling water tubes 130b is blown by the blower 16C through the heat exchange fins 135b. Dissipate heat to.

The radiated cooling water flows from the cooling water inlet / outlet 161 of the air / cooling water heat exchanger 16B to the cooler 48a of the inverter 48. In the cooler 48a of the inverter 48, the cooling water receives heat from a plurality of semiconductor elements.

The cooling water that has passed through the cooler 48a flows into the cooler 46a of the motor generator 46. In the cooler 46a, the cooling water receives heat from the traveling electric motor. The cooling water that has passed through the cooler 46a flows to the pump 36b.

In this way, the cooling water from the pump 36b flows in the order of air / cooling water heat exchanger 16B → cooler 48a → cooler 46a → pump 36b, so that the heat generated by the inverter 48 and the motor generator 46 is air / cooling water. It will be discharged from the heat exchanger 16B into the air stream.
On the other hand, in the air / refrigerant heat exchanger 16A, when the high-pressure refrigerant flows through the plurality of refrigerant tubes 130a, the high-pressure refrigerant in the plurality of refrigerant tubes 130a dissipates heat to the air flow through the plurality of heat exchange fins 135a.

For example, during cooldown in summer, the amount of heat to be dissipated from the high-pressure refrigerant to the air flow (that is, the cooling load) is large in the air / refrigerant heat exchanger 16A, and the cooling water is cooled in the air / cooling water heat exchanger 16B. When the amount of heat to be dissipated from (that is, the cooling load) is small, the result is as follows.
That is, in the air / refrigerant heat exchanger 16A, heat from the high-pressure refrigerant is released from the refrigerant tube 130a to the air stream through the plurality of heat exchange fins 135a.

In addition, heat from the high pressure refrigerant flows from the refrigerant tube 130a of the air / refrigerant heat exchanger 16A through the plurality of heat exchange fins 135a, the connection 135c and the heat exchange fins 135b of the air / cooling water heat exchanger 16B. Is released to.

From the above, the high-pressure refrigerant radiates heat to the air flow through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B. Here, as described above, in the chiller 24, the heat generated from the secondary battery 44a is released to the refrigerant. Therefore, the heat generated from the secondary battery 44a is released to the air flow through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

(Heating mode)
Next, the heating mode will be described with reference to FIG. In the heating mode (that is, the second mode), the electronic control device 32 opens the on-off valves 38a and 38c, respectively, as shown in FIG. In addition to this, the electronic control device 32 controls the throttle opening degrees of the expansion valves 20a and 20b, respectively.

The electronic control device 32 controls the three-way valve 14 to close the refrigerant inlet of the air / refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12 to open the bypass refrigerant passage 18. The electronic control device 32 controls the blower 16C to generate an air flow passing through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

Further, the electronic control device 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Along with this, the high-pressure refrigerant discharged from the compressor 10 passes through the indoor condenser 12.

In this case, the air mix door 5 opens the air inlet of the indoor condenser 12 to close the bypass passage 3. Therefore, the cold air from the evaporator 20 flows to the chamber condenser 12.

Therefore, in the indoor condenser 12, the high-pressure refrigerant dissipates heat to the air flow. As a result, warm air is blown from the indoor condenser 12 toward the vehicle interior.

On the other hand, the refrigerant that has passed through the indoor condenser 12 flows to the expansion valves 20a and 20b through the three-way valve 14 and the bypass refrigerant passage 18. That is, the refrigerant that has passed through the indoor condenser 12 does not flow into the air / refrigerant heat exchanger 16A.

The refrigerant flowing from the indoor condenser 12 to the expansion valve 20a through the three-way valve 14 and the bypass refrigerant passage 18 is depressurized by the expansion valve 20a. The refrigerant decompressed by the expansion valve 20a flows to the evaporator 20. In the evaporator 20, the refrigerant is sucked from the air flow blown from the blower 4 and evaporated.

The pressure of this evaporated refrigerant is adjusted by the pressure regulating valve 28. The pressure-adjusted refrigerant flows through the accumulator 26.

On the other hand, of the high-pressure refrigerant that has passed through the three-way valve 14 and the bypass refrigerant passage 18, the remaining refrigerant other than the refrigerant that flows through the expansion valve 20a flows through the expansion valve 20b. The flowing refrigerant is depressurized by the expansion valve 20b.

The refrigerant decompressed by the expansion valve 20b flows to the chiller 24. In this chiller 24, the refrigerant absorbs heat from the cooling water and evaporates. This evaporated refrigerant flows to the accumulator 26. The refrigerant flowing through the accumulator 26 is separated into a liquid phase refrigerant and a gas phase refrigerant, and the liquid phase refrigerant flows into the refrigerant inlet of the compressor 10.

In this way, the refrigerant flows in the order of compressor 10 → indoor condenser 12 → three-way valve 14 → bypass refrigerant passage 18 → expansion valve 20a → evaporator 20 → pressure regulating valve 28 → accumulator 26 → compressor 10. In addition to this, the refrigerant from the air / refrigerant heat exchanger 16A flows in the order of expansion valve 20b → chiller 24 → accumulator 26.

The electronic control device 32 controls the three-way valve 40 to close between the cooling water outlet of the pump 36b and the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B, and closes the cooling water outlet of the pump 36b and the battery unit. The space between the heat exchanger 44b of 44 and the cooling water inlet / outlet 70 of 44b is opened.

In the cooling water circuit 51, the cooling water flowing from the pump 36b flows in the order of the three-way valve 40 → the heat exchanger 44b of the battery unit 44 → the cooler 48a of the inverter 48 → the cooler 46a of the motor generator 46 → the pump 36b.

In the cooler 48a of the inverter 48, the cooling water receives heat from a plurality of semiconductor elements. In the cooler 46a of the motor generator 46, the cooling water receives heat from the traveling electric motor. Therefore, the heat received in the cooling water from the plurality of semiconductor elements in the cooler 48a and the heat received in the cooling water from the traveling electric motor in the cooler 46a are released to the secondary battery 44a via the heat exchanger 44b. become.

From the above, the secondary battery 44a is heated by the heat generated by the traveling electric motor and the plurality of semiconductor elements. Therefore, the output voltage of the secondary battery 44a can be increased in extremely cold weather. The electronic control device 32 stops the electric heater 42.

In the cooling water circuit 53, the cooling water flowing from the pump 36a flows to the chiller 24. In this chiller 24, the refrigerant absorbs heat from the cooling water. After the absorbed cooling water passes through the on-off valve 38a, it flows to the cooling water inlet / outlet 161 of the air / cooling water heat exchanger 16B. In this air / cooling water heat exchanger 16B, the cooling water absorbs heat from the air flow blown by the blower 16C.

The cooling water absorbed from this air flow flows into the pump 36a through the on-off valve 38c. Therefore, the cooling water flows in the order of pump 36a → chiller 24 → on-off valve 38a → air / cooling water heat exchanger 16B → on-off valve 38c → pump 36a.

As a result, in the air / cooling water heat exchanger 16B, the cooling water dissipates the heat absorbed from the air flow from the chiller 24 to the refrigerant.

At this time, in the air / cooling water heat exchanger 16B, the cooling water absorbs heat from the air flow through the plurality of heat exchange fins 135b and the cooling water tube 130b.

Further, as described above, the three-way valve 14 closes the refrigerant inlet of the air / refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12. Therefore, no refrigerant is circulated in the refrigerant tube 130a of the air / refrigerant heat exchanger 16A.

Therefore, the cooling water absorbs heat from the air flow through the plurality of heat exchange fins 135a, the connection portion 135c, the plurality of heat exchange fins 135b, and the cooling water tube 130b. That is, the cooling water absorbs heat from the air flow through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

Here, the electronic control device 32 determines whether or not the cooling water temperature is equal to or higher than the threshold value based on the detection signals of the cooling water temperature sensors 50b and 50c. The electronic control device 32 closes the on-off valves 38b and 38d when the cooling water temperature is below the threshold value.

On the other hand, the electronic control device 32 opens the on-off valves 38b and 38d when the cooling water temperature is equal to or higher than the threshold value. Along with this, of the cooling water from the pump 36b, the remaining cooling water other than the cooling water flowing to the heat exchanger 44b of the battery unit 44 is the on-off valve 38d → pump 36a → chiller 24 → on-off valve 38b → cooling of the inverter 48. It flows in the order of the vessel 48a.

As described above, a part of the heat generated by the motor generator 46 and the inverter 48 is dissipated to the battery unit 44. Of the heat generated from the motor generator 46 and the inverter 48, the remaining heat other than the heat radiated to the battery unit 44 is radiated from the chiller 24 to the refrigerant.

In this way, the electronic control device 32 intermittently opens the on-off valves 38b and 38d in accordance with the determination of whether or not the cooling water temperature is equal to or higher than the threshold value. Therefore, the heat generated from the motor generator 46 and the inverter 48 is intermittently transferred to the refrigerant through the chiller 24. As a result, the temperature of the cooling water flowing through the cooling water circuit 51 can be kept below the threshold value.

In the heating mode of the present embodiment, when the on-off valves 38b and 38d are opened, a part of the cooling water in the cooling water circuit 53 cools the inverter 48 in the cooling water circuit 51 as shown by the dotted arrow. It flows into the vessel 48a.

(Heater mode)
Next, the heater mode will be described with reference to FIG. The electronic control device 32 closes the on-off valves 38a and 38c, respectively. In addition to this, the electronic control device 32 closes the refrigerant passage between the bypass refrigerant passage 18 and the refrigerant inlet of the evaporator 20 by the expansion valve 20a. The electronic control device 32 controls the expansion valve 20b to adjust the flow path cross-sectional area of the refrigerant passage between the bypass refrigerant passage 18 and the chiller 24.

That is, the electronic control device 32 closes the expansion valve 20a and opens the expansion valve 20b.

The electronic control device 32 controls the three-way valve 14 to close the refrigerant inlet of the air / refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12 to open the bypass refrigerant passage 18. The electronic control device 32 stops the blower 16C.

Further, the electronic control device 32 operates the electric heater 42. The electronic control device 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Along with this, the high-pressure refrigerant discharged from the compressor 10 passes through the indoor condenser 12.

In this case, the air mix door 5 opens the air inlet of the indoor condenser 12 to close the bypass passage 3. Therefore, the cold air from the evaporator 20 flows to the chamber condenser 12.

Therefore, in the indoor condenser 12, the air flow receives heat from the high-pressure refrigerant. As a result, warm air is blown from the indoor condenser 12 toward the vehicle interior.

On the other hand, the refrigerant that has passed through the indoor condenser 12 flows to the expansion valve 20b through the three-way valve 14 and the bypass refrigerant passage 18. The refrigerant flowing through the expansion valve 20b is depressurized by the expansion valve 20b.

The refrigerant decompressed by the expansion valve 20b flows to the chiller 24. In this chiller 24, the refrigerant absorbs heat from the cooling water and evaporates. This evaporated refrigerant flows to the accumulator 26. The refrigerant flowing through the accumulator 26 is separated into a liquid phase refrigerant and a gas phase refrigerant, and the liquid phase refrigerant flows into the refrigerant inlet of the compressor 10.

In this way, the refrigerant flows in the order of compressor 10 → indoor condenser 12 → three-way valve 14 → expansion valve 20b → chiller 24 → accumulator 26. No refrigerant flows from the chamber condenser 12 to the evaporator 20 through the expansion valve 20b.

The electronic control device 32 controls the three-way valve 40 to close between the cooling water outlet of the pump 36b and the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B, and closes the cooling water outlet of the pump 36b and the battery unit. The space between the heat exchanger 44b of 44 and the cooling water inlet / outlet 70 of 44b is opened.

Here, some of the cooling water flowing out of the pump 36b flows in the order of the three-way valve 40 → the heat exchanger 44b → the cooler 48a → the cooler 46a → the pump 36b. In the heat exchanger 44b, the cooling water is heated from the electric heater 42.

As a result, the heat generated by the inverter 48 and the motor generator 46 and the heat generated by the electric heater 42 are released to the secondary battery 44a of the battery unit 44.

Of the cooling water flowing from the pump 36b to the three-way valve 40, the remaining cooling water other than the cooling water flowing to the heat exchanger 44b is pump 36b → three-way valve 40 → on-off valve 30d → pump 36a → chiller 24 → on-off valve 38b → cooling. It flows in the order of the vessel 48a.

As a result, of the heat generated by the inverter 48 and the motor generator 46, the remaining heat other than the heat released to the battery unit 44 is released from the chiller 24 to the refrigerant.

That is, a part of the heat generated by the inverter 48 and the motor generator 46 is released from the chiller 24 to the refrigerant.

In this way, the heat released from the cooling water to the refrigerant and the heat given to the refrigerant from the compressor 10 in the chiller 24 are radiated from the indoor condenser 12 to the air flow.

That is, the heat absorbed by the refrigerant from the cooling water and the heat given to the refrigerant by the compressor 10 are used to heat the air in the vehicle interior.

(Defrost mode)
Next, the defrosting mode will be described with reference to FIG. In the defrosting mode (that is, the third mode), the electronic control device 32 closes the on-off valves 38a and 38c, respectively, and opens the on-off valves 38b and 38d, respectively. In addition to this, the electronic control device 32 closes the refrigerant passage between the bypass refrigerant passage 18 and the refrigerant inlet of the evaporator 20 by the expansion valve 20a.
The electronic control device 32 controls the expansion valve 20b to adjust the flow path cross-sectional area of the refrigerant passage between the bypass refrigerant passage 18 and the chiller 24. That is, the electronic control device 32 closes the expansion valve 20a and opens the expansion valve 20b.

The electronic control device 32 controls the three-way valve 14 to open the refrigerant inlet of the air / refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12, and close the bypass refrigerant passage 18. The electronic control device 32 stops the blower 16C.

Further, the electronic control device 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Along with this, the high-pressure refrigerant discharged from the compressor 10 passes through the indoor condenser 12.

Therefore, the high-pressure refrigerant that has passed through the indoor condenser 12 flows through the three-way valve 14 to the air / refrigerant heat exchanger 16A. The refrigerant that has passed through the air / refrigerant heat exchanger 16A flows to the expansion valve 20b.

The refrigerant flowing through the expansion valve 20b is depressurized by the expansion valve 20b. The refrigerant decompressed by the expansion valve 20b flows to the chiller 24. In this chiller 24, the refrigerant absorbs heat from the cooling water and evaporates.
This evaporated refrigerant flows to the accumulator 26. The refrigerant flowing through the accumulator 26 is separated into a liquid phase refrigerant and a gas phase refrigerant, and the vapor phase refrigerant flows into the refrigerant inlet of the compressor 10.

In this way, the refrigerant flows in the order of compressor 10 → indoor condenser 12 → three-way valve 14 → air / refrigerant heat exchanger 16A → expansion valve 20b → chiller 24 → accumulator 26 → compressor 10.

Here, in the cooling water circuit 50, the cooling water flowing out from the pump 36a flows into the chiller 24. In this chiller 24, the cooling water is endothermic from the refrigerant. The endothermic cooling water flows in the order of on-off valve 38b → heat exchanger 44b → on-off valve 38d → pump 36a.

Therefore, in the heat exchanger 44b, the cooling water receives the heat generated from the electric heater 42. Therefore, the cooling water received from the electric heater 42 dissipates heat to the refrigerant in the chiller 24. That is, the heat given to the cooling water from the electric heater 42 is transferred to the refrigerant via the chiller 24.

Therefore, the heat absorbed by the refrigerant from the cooling water in the chiller 24 and the heat as the amount of work given to the refrigerant by the compressor 10 are transferred to the air / refrigerant heat exchanger 16A.

At this time, heat from the high-pressure refrigerant in the air / refrigerant heat exchanger 16A passes through the plurality of heat exchange fins 135a and the connection portion 135c from the plurality of refrigerant tubes 130a, and the plurality of heat exchange fins of the air / cooling water heat exchanger 16B. It is transmitted to 135a. Therefore, the heat from the high-pressure refrigerant melts the frost adhering to the heat exchange core 120c of the air / cooling water heat exchanger 16B.

As a result, the heat given to the cooling water from the electric heater 42 and the heat given to the refrigerant from the compressor 10 function to defrost the air / cooling water heat exchanger 16B. The electronic control device 32 stops the pump 36b and the blower 16C.

According to the present embodiment described above, the heat exchange fins 135a of the air / refrigerant heat exchanger 16A and the heat exchange fins 135b of the air / cooling water heat exchanger 16B are connected by the connecting portion 135c.

In the cooling mode, the cooling water in the air / cooling water heat exchanger 16B dissipates heat to the air flow. The refrigerant in the air / refrigerant heat exchanger 16A dissipates heat to the air flow through the connection portion 135c and the air / cooling water heat exchanger 16B.

That is, the refrigerant dissipates heat to the air flow through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B. Therefore, it is possible to improve the heat dissipation efficiency of radiating heat from the refrigerant to the air flow.

In the heating mode, the cooling water in the air / cooling water heat exchanger 16B absorbs heat from the air flow via the connection portion 135c and the air / refrigerant heat exchanger 16A. That is, the cooling water absorbs heat from the air flow via the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B. Therefore, the endothermic efficiency at which the cooling water absorbs heat from the air flow can be improved.

From the above, it is possible to provide the vehicle-mounted heat management device 1 in which the heat exchange efficiency of the outdoor unit 16 is improved.

In the heat pump system of Patent Document 1, the condensing portion is formed by a plurality of refrigerant tubes for passing refrigerant, a distribution tank for distributing the refrigerant to the plurality of refrigerant tubes, and a recovery tank for recovering the refrigerant passing through the plurality of refrigerant tubes. In the case of configuration, the following problems occur.

That is, during heating, gas-liquid two-phase refrigerant flows from the distribution tank to each of the plurality of refrigerant tubes. Here, when the ratio of the liquid-phase refrigerant to the gas-liquid two-phase refrigerant is extremely small, the gas-phase refrigerant hinders the liquid-phase refrigerant from being evenly distributed from the distribution tank to the plurality of refrigerant tubes.

Therefore, of the plurality of refrigerant tubes, the refrigerant tube having a small liquid phase refrigerant flow rate cannot sufficiently absorb heat from the outside air as the refrigerant evaporates.

From the above, when the outdoor unit functions as an evaporator during heating, the heat exchange efficiency when the refrigerant absorbs heat from the outside air in the outdoor unit decreases.

On the other hand, in the present embodiment, the refrigerant from the compressor 10 does not flow to the air / refrigerant heat exchanger 16A during heating. Therefore, in the air / refrigerant heat exchanger 16A as an outdoor unit, the above-mentioned problem that the heat exchange efficiency is lowered does not occur in the first place.

In the heater mode of the present embodiment, the heat generated by the inverter 48, the motor generator 46, and the electric heater 42 and the heat given to the refrigerant by the compressor 10 are radiated from the indoor capacitor 12 to the air flow.
Therefore, more heat can be released from the indoor condenser 12 to the air flow than when only the heat given to the refrigerant from the compressor 10 is dissipated from the indoor condenser 12 to the air flow.

In the defrosting mode of the present embodiment, the heat from the electric heater 42 and the heat given to the refrigerant from the compressor 10 are transferred from the refrigerant in the air / refrigerant heat exchanger 16A through the connection portion 135c to the air / cooling water heat exchanger 16B. Is given to the heat exchange core 120c of.

Therefore, in the present embodiment, a larger amount of heat can be given to the heat exchange core 120c as compared with the case where only the heat given to the refrigerant from the compressor 10 is given to the heat exchange core 120c. Therefore, the frost adhering to the heat exchange core 120c can be satisfactorily melted.

(Second Embodiment)
In the first embodiment, an example has been described in which the vehicle-mounted heat management device 1 includes an on-off valve 38d that opens and closes between the refrigerant outlet of the pump 36b and the refrigerant inlet of the pump 36a.

However, instead of this, the vehicle-mounted heat management device 1 includes a second embodiment including a regulating valve 38e that continuously adjusts the cross-sectional area of the refrigerant flow path between the refrigerant outlet of the pump 36b and the refrigerant inlet of the pump 36a. Will be described with reference to FIG.

In FIG. 10, the same reference numerals as those in FIG. 1 indicate the same ones, and the description thereof will be omitted.

The vehicle-mounted heat management device 1 of the present embodiment uses a regulating valve 38e instead of the on-off valve 38d of FIG.

The adjusting valve 38e includes a valve body that continuously adjusts the cross-sectional area of the refrigerant flow path between the refrigerant outlet of the pump 36b and the refrigerant inlet of the pump 36a, and an electric actuator that drives the valve body. The valve body is controlled by the electronic control device 32 via an electric actuator.

The electronic control device 32 controls the adjusting valve 38e so that the higher the cooling water temperature, the larger the cross-sectional area of the refrigerant flow path, based on the detection signals of the cooling water temperature sensors 50b and 50c.

On the other hand, the electronic control device 32 controls the adjusting valve 38e so that the cross-sectional area of the refrigerant flow path becomes smaller as the cooling water temperature becomes lower based on the detection signals of the cooling water temperature sensors 50b and 50c.
Therefore, in the heating mode, the higher the cooling water temperature, the more the amount of cooling water flowing from the pump 36b to the chiller 24 through the pump 36a can be increased. The lower the cooling water temperature, the smaller the amount of cooling water flowing from the pump 36b to the chiller 24 through the pump 36a.

From the above, the higher the cooling water temperature, the more heat is radiated from the chiller 24 to the refrigerant. Therefore, the temperature of the cooling water flowing through the heat exchanger 44b of the battery unit 44 can be accurately kept within a predetermined range.

According to the present embodiment described above, the vehicle-mounted heat management device 1 passes through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B from the refrigerant in the cooling mode as in the first embodiment. Dissipate heat to the air flow. In the heating mode, the cooling water is endothermic from the air stream via the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

From the above, it is possible to provide the vehicle-mounted heat management device 1 having improved heat exchange efficiency of the outdoor unit 16 as in the first embodiment.

(Third Embodiment)
In the first embodiment, in the outdoor unit 16 of the in-vehicle heat management device 1, the air / cooling water heat exchanger 16B is arranged on the upstream side in the air flow direction with respect to the air / refrigerant heat exchanger 16A. As described above, instead of this, the following may be used.

That is, in the third embodiment, as shown in FIG. 11, the air / cooling water heat exchanger 16B is arranged on the downstream side in the air flow direction with respect to the air / refrigerant heat exchanger 16A. In this case, the connection portion 135c is configured on the windward side of the air / cooling water heat exchanger 16B.

Therefore, in the heating mode, when the air / cooling water heat exchanger 16B absorbs heat from the outside air, frost is formed so as to spread from the heat exchange fin 135b side of the air / cooling water heat exchanger 16B to the connection portion 135c side. ..

As a result, frost is formed thinner on the heat exchange fins 135b than when the connection portion 135c is formed on the leeward side of the air / cooling water heat exchanger 16B. Along with this, the air flow path formed by the heat exchange fins 135b is suppressed from being blocked by frost. Therefore, the heat exchange between the air and the cooling water via the heat exchange fins 135b is maintained, so that the heating performance can be maintained for a long time.

Note that the present embodiment and the above-mentioned first embodiment differ only in the configuration of the outdoor unit 16, and the other configurations are the same. In FIG. 11, the same reference numerals as those in FIG. 1 indicate the same reference numerals, and the description thereof will be omitted.

According to the present embodiment described above, in the cooling mode, the refrigerant dissipates heat to the air flow through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B, as in the first embodiment. In the heating mode, the cooling water is endothermic from the air stream via the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

From the above, it is possible to provide the vehicle-mounted heat management device 1 having improved heat exchange efficiency of the outdoor unit 16 as in the first embodiment.

(Fourth Embodiment)
In the first embodiment, an example in which the in-vehicle heat management device 1 uses the indoor condenser 12 in which the refrigerant dissipates heat to the air flow as the heat exchanger for heating in the indoor air-conditioning casing 2 has been described.

However, instead of this, the fourth embodiment using the heater core 61 in which the hot water dissipates heat to the air flow in the in-vehicle heat management device 1 will be described with reference to FIG.

As shown in FIG. 12, the vehicle-mounted heat management device 1 of the present embodiment includes a hot water circuit 60 including a heater core 61.

The vehicle-mounted heat management device 1 of the present embodiment includes a hot water circuit 60 instead of the indoor condenser 12 of FIG.

The configuration of the vehicle-mounted heat management device 1 of the present embodiment other than the hot water circuit 60 is the same as that of the vehicle-mounted heat management device 1 of the first embodiment. In FIG. 12, the same reference numerals as those in FIG. 1 indicate the same reference numerals, and the description thereof will be omitted.

Therefore, the hot water circuit 60 of the in-vehicle heat management device 1 of the present embodiment will be mainly described. The hot water circuit 60 includes a water / refrigerant heat exchanger 62 and a pump 63 together with a heater core 61. The heater core 61, the water / refrigerant heat exchanger 62, and the pump 63 are connected by a hot water pipe to form a closed circuit for circulating hot water. The heater core 61 is arranged in the indoor air conditioning casing 2.

The pump 63 circulates hot water in the order of pump 63 → heater core 61 → water / refrigerant heat exchanger 62 → pump 63. The heater core 61 dissipates hot water to the cold air that has passed through the evaporator 20.

In the water / refrigerant heat exchanger 62, the hot water that has passed through the heater core 61 is the first radiator that absorbs heat from the refrigerant. The endothermic hot water is sucked into the pump 63. The pump 63 allows hot water to flow toward the water / refrigerant heat exchanger 62.

The water / refrigerant heat exchanger 62 is arranged between the refrigerant outlet of the compressor 10 and the refrigerant inlet of the three-way valve 14. The water / refrigerant heat exchanger 62 is a heat exchanger that dissipates heat from the high-pressure refrigerant from the compressor 10 to hot water.

As a result, hot water circulates between the water / refrigerant heat exchanger 62 and the heater core 61, so that the hot water absorbed from the high-pressure refrigerant in the water / refrigerant heat exchanger 62 dissipates heat from the heater core 61 to cold air.

Therefore, the heater core 61 heats the cold air blown from the evaporator 20 with hot water. As a result, the warm air heated by the heater core 61 is blown into the vehicle interior.

According to the present embodiment described above, in the vehicle-mounted heat management device 1, the refrigerant passes through the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B in the cooling mode as in the first embodiment. Dissipate heat to the air flow. In the heating mode, the cooling water is endothermic from the air stream via the air / refrigerant heat exchanger 16A and the air / cooling water heat exchanger 16B.

As described above, also in the present embodiment including the hot water circuit 60 instead of the indoor condenser 12, the vehicle-mounted heat management device 1 is provided so as to improve the heat exchange efficiency of the outdoor unit 16 as in the first embodiment. be able to.

(Fifth Embodiment)
In the first embodiment, the defrosting mode in which the vehicle-mounted heat management device 1 melts the frost on the air / cooling water heat exchanger 16B using the high-pressure refrigerant has been described.

In addition to this, the fifth embodiment for carrying out the defrosting mode in which the cooling water melts the frost that has reached the air / cooling water heat exchanger 16B will be described with reference to FIG.

The vehicle-mounted heat management device 1 of the present embodiment has the same configuration as the vehicle-mounted heat management device 1 of the first embodiment. The vehicle-mounted heat management device 1 of the present embodiment and the vehicle-mounted heat management device 1 of the first embodiment differ only in the operation of the defrost mode, and the other operations are the same as each other. Therefore, the defrosting mode in the vehicle-mounted heat management device 1 of the present embodiment will be described.

First, the electronic control device 32 closes the on-off valves 38a and 38c, respectively, and opens the on-off valves 38b and 38d, respectively. In addition to this, the electronic control device 32 closes the refrigerant passage between the bypass refrigerant passage 18 and the refrigerant inlet of the evaporator 20 by the expansion valve 20a.
The electronic control device 32 controls the expansion valve 20b to adjust the flow path cross-sectional area of the refrigerant passage between the bypass refrigerant passage 18 and the chiller 24. That is, the electronic control device 32 closes the expansion valve 20a and opens the expansion valve 20b.

The electronic control device 32 controls the three-way valve 14 to close the refrigerant inlet of the air / refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12 to open the bypass refrigerant passage 18. The electronic control device 32 stops the blower 16C. The electronic control device 32 operates the pumps 36a and 36b.

The electronic control device 32 controls the three-way valve 40 to open a space between the cooling water outlet of the pump 36b and the cooling water inlet / outlet 160 of the air / cooling water heat exchanger 16B, and opens the cooling water outlet of the pump 36b and the battery unit. Close the space between the heat exchanger 44b 44 and the cooling water inlet / outlet 70.

Further, the electronic control device 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10.

Along with this, the high-pressure refrigerant discharged from the compressor 10 flows in the order of the indoor condenser 12 → the three-way valve 14 → the bypass refrigerant passage 18 → the expansion valve 20b → the chiller 24 → the accumulator 26 → the compressor 10.

At this time, the cooling water flowing out from the pump 36a flows in the cooling water circuit 50 in the order of the chiller 24 → on-off valve 38b → cooler 42a → on-off valve 38d → pump 36a. Therefore, the heat generated from the electric heater 42 is dissipated from the chiller 24 to the refrigerant. The heat radiated to this refrigerant is given to the air flow in the indoor air conditioning casing 2 from the indoor condenser 12.

In addition to this, the cooling water flowing out from the pump 36b flows in the cooling water circuit 52 in the order of the three-way valve 40 → air / cooling water heat exchanger 16B → cooler 48a → cooler 46a → pump 36b.

Here, in the cooler 48a, the cooling water absorbs heat from a plurality of semiconductor elements. In the cooler 46a, the cooling water absorbs heat from the traveling electric motor. Therefore, the heat generated from the inverter 48 and the motor generator 46 is transferred to the air / cooling water heat exchanger 16B by the cooling water.

From the above, the heat generated from the inverter 48 and the motor generator 46 is given to the air / cooling water heat exchanger 16B via the cooling water. Therefore, the heat from the cooling water can melt the frost adhering to the air / cooling water heat exchanger 16B.

According to the present embodiment described above, in the cooling mode, the air / refrigerant heat exchanger 16A dissipates heat from the refrigerant through the air / cooling water heat exchanger 16B. In the heating mode, the cooling water in the air / cooling water heat exchanger 16B absorbs heat via the air / refrigerant heat exchanger 16A.

In the present embodiment, in the defrosting mode, the heat generated from the inverter 48 and the motor generator 46 is given to the air / cooling water heat exchanger 16B via the cooling water. Therefore, in the present embodiment, the frost adhering to the heat exchange core 120c of the air / refrigerant heat exchanger 16A can be satisfactorily melted.

(Other embodiments)
(1) In the first to fifth embodiments described above, the vehicle-mounted heat management device 1 in which the heat management device according to the present disclosure is applied to an automobile has been described, but instead, the heat management device according to the present disclosure is used as an automobile. It may be applied to moving objects such as trains and airplanes other than the above. Alternatively, the heat management device according to the present disclosure may be applied to an installation type air conditioner such as a house or a building.

(2) In the first embodiment described above, an example of defrosting by the heat of the refrigerant flowing through the air / refrigerant heat exchanger 16A has been described as the defrosting mode. In the fifth embodiment, an example of defrosting by the heat of the cooling water as the defrosting mode has been described.

In addition to this, the defrosting mode in combination with the defrosting mode of the first embodiment and the defrosting mode of the fifth embodiment may be carried out. That is, a defrosting mode may be performed in which defrosting is performed by the heat of the refrigerant and defrosting is performed by the heat of the cooling water.

(3) In the first to fifth embodiments described above, an example in which cooling water is used as a heat medium has been described, but instead, something other than cooling water may be used as a heat medium.

(4) In the third embodiment, the air / refrigerant heat exchanger 16A is arranged on the upstream side of the air flow with respect to the air / cooling water heat exchanger 16B, and the refrigerant flowing through the air / refrigerant heat exchanger 16A is arranged. An example of defrosting the air / cooling water heat exchanger 16B by heat has been described.

However, instead of this, an air / refrigerant heat exchanger 16A is arranged on the upstream side of the air flow with respect to the air / cooling water heat exchanger 16B, and cooling is performed as a defrosting mode as in the fifth embodiment. It may be defrosted by the heat of water.

Alternatively, in a state where the air / refrigerant heat exchanger 16A is arranged on the upstream side of the air flow with respect to the air / cooling water heat exchanger 16B, it is removed by the heat of the refrigerant and the heat of the cooling water in the same manner as in (2) above. A defrosting mode in which frost is carried out may be carried out.

(5) In the first to fifth embodiments described above, an example in which the high-pressure refrigerant discharged from the compressor 10 is passed through the indoor condenser 12 in the cooling mode has been described. However, instead of this, the high-pressure refrigerant discharged from the compressor 10 may bypass the indoor condenser 12 and flow to the air / refrigerant heat exchanger 16A.

(6) In the first to fifth embodiments described above, an example in which the refrigerant is passed through the evaporator 20 in the heating mode has been described, but instead, in the heating mode, the flow of the refrigerant through the evaporator 20 may be stopped. Good.

(7) In the first to fifth embodiments, an example using a cooling water circuit 52 for dissipating heat generated by the motor generator 46 and the inverter 48 from the air / cooling water heat exchanger 16B to the air flow will be described. did. However, instead of this, the cooling water circuit 52 may be deleted.

(8) The present disclosure is not limited to the above-described embodiment, and can be changed as appropriate. Further, the above-described embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential and when they are clearly considered to be essential in principle. No. Further, in each of the above embodiments, when numerical values such as the number, numerical values, amounts, and ranges of the constituent elements of the embodiment are mentioned, when it is clearly stated that they are particularly essential, and in principle, the number is clearly limited to a specific number. It is not limited to the specific number except when it is done. In addition, in each of the above embodiments, when referring to the shape, positional relationship, etc. of a component or the like, the shape, unless otherwise specified or limited in principle to a specific shape, positional relationship, etc. It is not limited to the positional relationship.

In the first to fifth embodiments and other embodiments, the heat management device includes a blower that generates an air flow that passes through the radiator and the second radiator. In the first mode, the second radiator dissipates heat from the refrigerant to the air flow via the radiator while the blower is generating the air flow.

In the second mode, the radiator absorbs heat from the air flow through the second radiator while the blower is generating the air flow. In the third mode, the second radiator dissipates heat from the refrigerant to the radiator with the blower stopping the generation of airflow.

Further, the heat management device includes an on-off valve that opens and closes between the chiller and the radiator in the first heat medium circuit.

In the first mode, the second radiator dissipates heat from the refrigerant to the air flow via the radiator with the on-off valve closed between the chiller and the radiator. In the third mode, the second radiator dissipates heat from the refrigerant to the radiator with the on-off valve open between the chiller and the radiator.

(Summary)
According to the first aspect described in the first to fifth embodiments and a part or all of the other embodiments, the heat management device is a compressor that sucks in and compresses and discharges the refrigerant, and the compressor. It includes a first radiator that dissipates heat from the discharged refrigerant.

The heat management device includes a second radiator that dissipates heat from the refrigerant that has passed through the first radiator to the air flow, a first pressure reducing valve and a second pressure reducing valve that reduce the pressure of the refrigerant that has passed through the first radiator, and a first pressure reducing device. It is provided with an evaporator that evaporates the refrigerant that has passed through the valve.

The heat management device includes a chiller that evaporates the refrigerant that has passed through the second pressure reducing valve by absorbing heat from the heat medium, and the first pressure reducing valve and the second pressure reducing valve that bypasses the second radiator for the refrigerant that has passed through the first radiator. It is provided with a bypass refrigerant passage that flows through the pressure reducing valve.

The heat management device includes a switching valve that sets one of the first state and the second state. The first state is a state in which the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator are opened and the bypass refrigerant passage is closed. The second state is a state in which the space between the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator is closed and the bypass refrigerant passage is opened.

The heat management device includes a radiator for exchanging heat between the heat medium and the air flow, and a heat medium circuit for circulating the heat medium between the chiller and the radiator.

In the first mode in which the switching valve is set to the first state, the refrigerant in the second radiator dissipates heat to the air flow via the radiator. In the second mode in which the heat medium in the heat medium circuit circulates with the switching valve set to the second state, the heat medium in the radiator absorbs heat from the air flow via the second radiator.

According to the second viewpoint, the heat management device includes a connection portion for connecting the second radiator and the radiator.

In the first mode in which the switching valve is set to the first state, the refrigerant in the second radiator dissipates heat to the air flow via the connection portion and the radiator.

In the second mode in which the heat medium in the heat medium circuit circulates with the switching valve set to the second state, the heat medium in the radiator absorbs heat from the air flow via the connection portion and the second radiator.

According to the third aspect, the heat management device is a first for circulating the heat medium between the heating element and the radiator when the heating element that dissipates heat to the heat medium and the heat medium circuit are the first heat medium circuit. It is provided with a two heat medium circuit.

In the first mode, the radiator dissipates heat to the air flow while the heat medium is circulating in the second heat medium circuit.

According to the fourth aspect, when the heating element is the first heating element, the heat management device circulates the heat medium between the second heating element that dissipates heat to the heating medium, the second heating element, and the chiller. The third heat medium circuit of the above is provided.

As a result, the heat generated by the second heating element can be transferred to the refrigerant via the chiller.

According to the fifth viewpoint, the heat management device and the radiator are arranged outdoors.

In the third mode in which the heat medium circulates in the third heat medium circuit with the switching valve set to the first state and the second heating element dissipates heat to the heat medium, the heat medium is supplied from the second heating element to the heat medium. The heat generated is transferred to the refrigerant through the chiller. The refrigerant in the second radiator dissipates heat to the radiator through the connection and melts the frost adhering to the radiator.

As a result, the heat generated by the second heating element can be used for defrosting the radiator.

According to the sixth viewpoint, the second radiator is arranged on the upstream side of the air flow with respect to the radiator.

According to the seventh viewpoint, the second radiator separates the condensing part that dissipates heat from the refrigerant to the heat medium to condense the refrigerant and the refrigerant that has passed through the condensing part into the liquid phase refrigerant and the gas phase refrigerant and liquid. It includes a gas-liquid separation unit that discharges the phase refrigerant and a supercooling unit that supercools the liquid-phase refrigerant discharged from the gas-liquid separation unit.

According to the eighth viewpoint, in the second mode, the first radiator dissipates heat from the refrigerant, and in the first mode, the second radiator dissipates heat from the refrigerant to the air flow.

Claims (8)

1. It is a heat management device
   A compressor (10) that sucks in refrigerant, compresses it, and discharges it.
   A first radiator (12) that dissipates heat from the refrigerant discharged from the compressor, and
   A second radiator (16A) that dissipates heat from the refrigerant that has passed through the first radiator to an air flow, and a first pressure reducing valve (20a) and a second pressure reducing valve that reduce the pressure of the refrigerant that has passed through the first radiator. (20b) and
   An evaporator (20) that evaporates the refrigerant that has passed through the first pressure reducing valve, and
   A chiller (24) that evaporates the refrigerant that has passed through the second pressure reducing valve by absorbing heat from the heat medium.
   A bypass refrigerant passage (18) that allows the refrigerant that has passed through the first radiator to bypass the second radiator and flow through the first pressure reducing valve and the second pressure reducing valve.
   The first state in which the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator are opened and the bypass refrigerant passage is closed, and the refrigerant outlet of the first radiator and the second heat dissipation. A switching valve (14) that closes between the refrigerant inlets of the vessel and sets the bypass refrigerant passage to either one of the second states.
   A radiator (16B) that exchanges heat between the heat medium and the air flow,
   A heat medium circuit (53) for circulating the heat medium between the chiller and the radiator is provided.
   In the first mode in which the switching valve is set to the first state, the refrigerant in the second radiator dissipates heat to the air flow via the radiator.
   In the second mode in which the heat medium in the heat medium circuit circulates with the switching valve set to the second state, the heat medium in the radiator passes through the air through the second radiator. A heat management device that absorbs heat from the flow.
2. A connection portion (135c) for connecting the second radiator and the radiator is provided.
   In the first mode in which the switching valve is set to the first state, the refrigerant in the second radiator dissipates heat to the air flow via the connection portion and the radiator.
   In the second mode in which the heat medium in the heat medium circuit circulates with the switching valve set to the second state, the heat medium in the radiator connects the connection portion and the second radiator. The heat management device according to claim 1, wherein heat is absorbed from the air flow through the air stream.
3. Heating elements (48, 46) that dissipate heat to the heat medium,
   When the heat medium circuit is a first heat medium circuit, a second heat medium circuit (52) for circulating the heat medium between the heating element and the radiator is provided.
   The heat management device according to claim 1 or 2, wherein in the first mode, the radiator dissipates heat to the air flow in a state where the heat medium is circulated in the second heat medium circuit.
4. When the heating element is a first heating element, a second heating element (42) that dissipates heat to the heating medium and
   The heat management device according to claim 3, further comprising a third heat medium circuit (50) for circulating the heat medium between the second heating element and the chiller.
5. The radiator is arranged outdoors and
   In the third mode in which the switching valve is set to the first state and the heat medium circulates in the third heat medium circuit in a state where the second heating element dissipates heat to the heat medium, the second mode. The heat applied to the heat medium from the heating element is transferred to the refrigerant via the chiller.
   The heat management device according to claim 4, wherein the refrigerant in the second radiator dissipates heat to the radiator to melt the frost adhering to the radiator.
6. The heat management device according to claim 4, wherein the second radiator is arranged on the upstream side of the air flow with respect to the radiator.
7. The second radiator
   A condensing unit (100) that dissipates heat from the refrigerant to the heat medium and condenses the refrigerant.
   A gas-liquid separation unit (120) that separates the refrigerant that has passed through the condensing unit into a liquid-phase refrigerant and a gas-phase refrigerant and discharges the liquid-phase refrigerant.
   A supercooling unit (110) that supercools the liquid phase refrigerant discharged from the gas-liquid separation unit, and
   The heat management device according to any one of claims 1 to 5.
8. In the second mode, the first radiator dissipates heat from the refrigerant.
   The heat management device according to any one of claims 1 to 7, wherein in the first mode, the second radiator dissipates heat from the refrigerant to the air flow.

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