CN114174736A - Thermal management device - Google Patents

Abstract

The heat management device is provided with: a first radiator (12) for radiating heat from the refrigerant discharged from the compressor; a second radiator (16A) for radiating the refrigerant discharged from the first radiator to the air flow; an evaporator (20) for evaporating the refrigerant; a chiller (24) that evaporates the refrigerant by absorbing heat from the heat medium; a bypass refrigerant passage (18) through which the refrigerant discharged from the first radiator bypasses the second radiator and flows to the evaporator and the cooler; a switching valve (14) set to either a first state for closing the bypass refrigerant passage or a second state for opening the bypass refrigerant passage; a radiator (16B) that exchanges heat between the heat medium and the air flow; and a heat medium circuit (53) for circulating the heat medium between the refrigerator and the radiator. In a first mode in which the refrigerant in the second radiator radiates heat to the airflow via the radiator in the first state, and in a second mode in which the heat medium in the heat medium circuit circulates in the second state, the heat medium in the radiator absorbs heat from the airflow via the second radiator.

Description

Thermal management device

Cross reference to related applications

The present application is based on japanese patent application No. 2019-136355, filed 24.7.2019, the contents of which are incorporated herein by reference.

Technical Field

The present invention relates to a thermal management device.

Background

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). In heating, the refrigerant discharged from the compressor flows in the order of the indoor condenser → the first expansion valve → the outdoor unit → the compressor. In 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, the outdoor unit functions as an evaporator that absorbs heat from the outside air to evaporate the refrigerant during heating. During cooling, the outdoor unit functions as a radiator that radiates heat from the refrigerant to the outside air to condense the refrigerant.

The outdoor unit is provided with: a condensing unit that condenses the refrigerant by radiating heat from the refrigerant to outside air; and a gas-liquid separation unit that separates the gas-liquid two-phase refrigerant that has passed through the condensation unit into a liquid-phase refrigerant and a gas-phase refrigerant, stores the gas-phase refrigerant, and discharges the liquid-phase refrigerant.

The outdoor unit includes a supercooling unit that supercools the liquid-phase refrigerant discharged from the gas-liquid separation unit by radiating the liquid-phase refrigerant to the outside air. Thus, by setting an appropriate supercooling degree in the refrigeration cycle, the heat exchange efficiency during cooling can be improved.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2014-113975

According to the studies of the present inventors, in the heat pump system described above, in order to improve the heat exchange efficiency during cooling, it is desirable that the cross-sectional area of the refrigerant flow path of the supercooling section be smaller than the cross-sectional area of the refrigerant flow path of the condensation section.

However, during heating, the gas-liquid two-phase refrigerant having a dryness close to 100% flows through the refrigerant passage having a small cross-sectional area in the subcooling portion. Therefore, the pressure loss generated when the refrigerant passes through the supercooling portion may be significantly increased. Therefore, when the outdoor unit is caused to function as an evaporator during heating, the heat exchange efficiency between the outside air and the refrigerant in the subcooling portion is reduced.

Disclosure of Invention

In view of the above, an object of the present invention is to provide a thermal management device that improves heat exchange efficiency.

According to one aspect of the present invention, a thermal management device includes: a compressor that sucks, compresses, and discharges a refrigerant;

a first radiator that radiates heat from the refrigerant discharged from the compressor;

a second radiator that radiates heat to the air flow from the refrigerant having passed through the first radiator;

a first pressure reducing valve and a second pressure reducing valve that reduce the pressure of the refrigerant after passing through the first radiator;

an evaporator that evaporates the refrigerant having passed through the first pressure reducing valve;

a chiller that evaporates the refrigerant having passed through the second pressure reducing valve by absorbing heat from the heat medium;

a bypass refrigerant passage for bypassing the refrigerant having passed through the first radiator around the second radiator and flowing into the first pressure reducing valve and the second pressure reducing valve;

a switching valve set to any one of a first state that opens between the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator and closes the bypass refrigerant passage and a second state that closes between the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator and opens the bypass refrigerant passage;

a radiator that exchanges heat between the thermal medium and the air flow; and

a heat medium circuit for circulating a heat medium between the refrigerator and the radiator,

in a first mode in which the switching valve is set to the first state, the refrigerant in the second radiator radiates heat to the air flow via the radiator,

in a second mode in which the heat medium in the heat medium circuit circulates in a state in which the switching valve is set to the second state, the heat medium in the radiator absorbs heat from the air flow via the second radiator.

Thereby, in the first mode, the refrigerant in the second radiator radiates heat to the air via the connection portion and the radiator. Therefore, the refrigerant can be made to radiate heat from the second radiator and the radiator to the air. Therefore, the heat exchange efficiency between the refrigerant and the air flow can be improved as compared with the case where only the second radiator refrigerant of the radiator and the second radiator radiates heat to the air.

In the second mode, the thermal medium of the radiator absorbs heat from the air via the second heat sink. The heat medium is thus able to absorb heat from the air via the radiator and the second heat sink. Therefore, the heat exchange efficiency between the heat medium and the air flow can be improved as compared with the case where only the radiator heat medium in the radiator and the second heat sink absorbs heat from the air flow.

Thus, a heat management device that improves heat exchange efficiency can be provided. In addition, the parenthesized reference numerals attached to the respective components and the like indicate examples of the correspondence between the components and the like and the specific components and the like described in the embodiments described later.

Drawings

Fig. 1 is a diagram showing the overall configuration of a refrigeration cycle and a cooling water circuit of an in-vehicle thermal management device according to a first embodiment.

Fig. 2 is a partially enlarged view for illustrating the arrangement relationship of the secondary battery, the cooler, and the electric heater in the battery unit in fig. 1.

Fig. 3 is a view showing the arrangement relationship of the heat exchange core and the tanks and the flow direction of the refrigerant in the air/refrigerant heat exchanger of the outdoor unit in fig. 1.

Fig. 4 is a view showing the arrangement relationship between the heat exchange cores and the tanks and the flow direction of the refrigerant in the air/cooling water heat exchanger of the outdoor unit in fig. 1.

Fig. 5 is a perspective view showing a 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.

Fig. 6 is a diagram showing the flow of the refrigerant in the refrigeration cycle and the flow of the cooling water in the cooling water circuit in the cooling mode in the first embodiment.

Fig. 7 is a diagram showing the flow of the refrigerant in the refrigeration cycle and the flow of the cooling water in the cooling water circuit in the heating mode in the first embodiment.

Fig. 8 is a diagram showing the flow of the refrigerant in the refrigeration cycle and the flow of the cooling water in the cooling water circuit in the heater mode in the first embodiment.

Fig. 9 is a diagram showing the flow of the refrigerant in the refrigeration cycle and the flow of the cooling water in the cooling water circuit in the defrosting mode in the first embodiment.

Fig. 10 is a diagram showing the overall configuration of the refrigeration cycle and the cooling water circuit of the in-vehicle thermal management device according to the second embodiment.

Fig. 11 is a diagram showing the overall configuration of the refrigeration cycle and the cooling water circuit of the in-vehicle thermal management device according to the third embodiment.

Fig. 12 is a diagram showing the overall configuration of the refrigeration cycle and the cooling water circuit of the in-vehicle thermal management device according to the fourth embodiment.

Fig. 13 is a diagram showing the overall configuration of the refrigeration cycle and the cooling water circuit of the in-vehicle thermal management device according to the fifth embodiment, and is a diagram showing the flow of the refrigerant in the refrigeration cycle and the flow of the cooling water in the cooling water circuit in the defrosting mode.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that, in the following embodiments, the same or equivalent portions are denoted by the same reference numerals for simplicity of description.

(first embodiment)

Fig. 1 shows a configuration of an in-vehicle thermal management device 1 according to a first embodiment.

As shown in fig. 1, the in-vehicle thermal 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, a chiller 24, an accumulator 26, and a pressure regulating valve 28.

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

The indoor condenser 12 is a first radiator that radiates 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 disposed in the indoor air conditioning casing 2.

The indoor air conditioning casing 2 constitutes an indoor air conditioning device for conditioning air in the vehicle interior together with the indoor condenser 12, the evaporator 20, the air mix door 5, the blower 4, and the like. Although an axial flow fan is illustrated as the blower 4 in fig. 1, a centrifugal fan may be used in practice, for example.

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

The air mix door 5 adjusts a ratio of an amount of air passing through the indoor condenser 12 to an amount of air passing through the bypass passage 3 among the cool air blown from the vaporizer 20 in the indoor air-conditioning case 2.

As the air mix door 5, various doors such as a film door, a slide door, a plate door, and a swing 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 through which the cool air from the vaporizer 20 in the indoor air conditioning casing 2 flows toward the vehicle interior while bypassing the indoor condenser 12.

The three-way valve 14 includes a valve body that connects one of 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 closes a gap between the other refrigerant inlet and the refrigerant outlet of the indoor condenser 12.

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

The three-way valve 14 of the present embodiment is a switching valve that is set to either one of a first state and a second state as described below. 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 open, and the bypass passage 3 is open.

The second 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 closed, and the bypass passage 3 is closed. The spool of the three-way valve 14 is driven by an electric actuator. The electric actuator is controlled by an electronic control device 32. Note that the electronic control unit 32 is referred to as an ECU in fig. 1.

The three-way valve 14 includes 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 a second refrigerant outlet connected to the refrigerant inlets of the expansion valves 20a and 20b, respectively.

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

Thus, the outdoor unit 16 is disposed outside (i.e., outdoors) 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 radiates heat from the refrigerant to the air flow by heat exchange between the refrigerant flowing in from the indoor condenser 12 through the three-way valve 14 and the air flow blown by the blower 16C.

As described later, the air/cooling water heat exchanger 16B is a radiator that performs heat exchange between cooling water and the air flow blown by the blower 16C. The cooling water is a heat medium for moving heat as described below. The air/cooling water heat exchanger 16B includes cooling water inlets and outlets 160 and 161 through which cooling water enters and exits.

In the present embodiment, as described below, 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 disposed on the vehicle traveling direction front side 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. Hereinafter, specific structures of the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B will be explained.

The blower 16C is disposed 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 in the engine compartment. The blower fan 16C is an electric fan for generating an air flow (i.e., an outside air flow) through the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B.

The air/cooling water heat exchanger 16B is disposed 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 a second refrigerant outlet of the three-way valve 14 and respective refrigerant inlets of the expansion valves 20a, 20 b. As described above, the second refrigerant outlet is a refrigerant outlet connected to the refrigerant inlet of each of the expansion valves 20a and 20b in the three-way valve 14.

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

The expansion valve 20a includes: a valve body that adjusts a flow path area (i.e., a throttle opening degree) of a refrigerant path between the refrigerant inlet of the evaporator 20 and the common connection portion 19 that bypasses the refrigerant path 18 and the refrigerant outlet of the air/refrigerant heat exchanger 16A; and an electric actuator that drives the valve element. The valve body is controlled by an electronic control unit 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 disposed on the upstream side of the indoor condenser 12 in the air flow direction in the indoor air conditioning casing 2. The evaporator 20 is a heat exchanger that exchanges heat between the refrigerant that has passed through the expansion valve 20a and the air flow, absorbs heat from the air flow, and evaporates the refrigerant.

The expansion valve 20b includes: a valve body that adjusts the flow path area (i.e., the throttle opening) of the refrigerant path between the bypass refrigerant path 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; and an electric actuator that drives the valve element.

The valve body is controlled by an electronic control unit 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 disposed in parallel with the refrigerant flow direction between a common connection 19, which bypasses the refrigerant passage 18 and 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 to cause the refrigerant to absorb heat from the cooling water.

The accumulator 26 is a gas-liquid separator for separating the two-phase gas-liquid refrigerant having passed through the chiller 24 or the evaporator 20 into a liquid-phase refrigerant and a gas-phase refrigerant, storing the liquid-phase refrigerant, and guiding the gas-phase refrigerant to the refrigerant inlet of the compressor 10. The pressure regulating valve 28 functions to bring the refrigerant pressure in the evaporator 20 close to a predetermined pressure and the refrigerant temperature in the evaporator 20 close to a predetermined temperature.

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

The chiller 24, the pump 36a, and the battery unit 44 together constitute cooling water circuits 50, 53 and the like. The pump 36a is a second pump for circulating 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 36 a.

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

As shown in fig. 2, battery unit 44 includes secondary battery 44a and heat exchanger 44 b. The secondary battery 44a stores dc power for supplying electric 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 through which cooling water enters and exits. Further, as described later, the direction of flow in the heat exchanger 44b changes depending on the operation.

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

The opening/closing 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 element. The valve body is controlled by an electronic control unit 32 via an electric actuator.

The opening/closing 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 element.

The pump 36b is a 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 36 b.

The inverter 48 is a first heat generator including a cooler 48a as a heat exchanger for radiating heat from a plurality of semiconductor elements constituting the inverter 48 to cooling water. In fig. 1 and the like, the inverter 48 is referred to as "INV".

The motor generator 46 is a first heat generator including a running motor for driving the driving wheels of the vehicle and a cooler 46 a. The running motor also functions as a generator that generates electric power by rotation of the drive wheels of the vehicle. The cooler 46a is a heat exchanger that radiates heat from the electric motor for running to the cooling water. The pump 36b is controlled by the electronic control device 32.

The chiller 24, together with the pump 36a and the air/cooling water heat exchanger 16B, constitutes a cooling water circuit 53. 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 → the on-off valve 38a → the air/cooling water heat exchanger 16B → the on-off valve 38c → the pump 36 a.

The three-way valve 40 opens a space between the cooling water outlet/inlet 160 of the air/cooling water heat exchanger 16B and one of the cooling water outlets/inlets 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 a space between the other 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 is controlled by the electronic control device 32.

The opening/closing 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 element.

The opening/closing 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 element. The opening and closing valves 38a, 38c are controlled by the electronic control unit 32.

The cooling water circuits 50, 51, and 52 configured as described above are provided with cooling water temperature sensors 50a, 50b, and 50 c.

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 of 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 unit 32 controls the on-off valves 38a, 38b, 38c, 38 d.

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

For convenience of explanation, fig. 3, 4, and 5 show examples in which XYZ coordinates are set. The X direction, the Y direction, and the Z direction in the XYZ coordinates are directions orthogonal to each other.

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

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

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

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

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

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

The gas-liquid separation portion 120 functions as a tank 111b that separates the refrigerant from the tank 101d into a gas-phase refrigerant and a liquid-phase refrigerant, stores the gas-phase refrigerant, and guides the liquid-phase refrigerant to the supercooling portion 110. The supercooling unit 110 is disposed on the other side in the Z direction with respect to the condensation unit 100. The supercooling unit 110 includes tanks 111a and 111b and a heat exchange passage 111 c.

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

The tank 111a has an effect of collecting the liquid-phase refrigerant having passed through the plurality of refrigerant tubes 130a of the heat exchange passage portion 111c and guiding the collected liquid-phase refrigerant to the expansion valves 20a and 20 b. The cross-sectional flow area of the plurality of refrigerant tubes 130a of the supercooling unit 110 of the present embodiment is smaller than the cross-sectional flow area of the plurality of refrigerant tubes 130a of the condensation unit 100.

The heat exchange passage portions 102a, 102b, 102c, and 111c of the present embodiment constitute the heat exchange core 140 together with the plurality of heat exchange fins 135a, respectively. The plurality of heat exchange fins 135a form a plurality of air flow paths through which the air flow passes 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 120 c.

The heat exchange core 120c includes a plurality of cooling water tubes 130b and a plurality of heat exchange fins 135b extending in the X direction. 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 the air flow passes in the Y direction.

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

Fig. 5 shows the arrangement relationship of the refrigerant tubes 130a and the cooling water tubes 130b and the heat exchange fins 135a and 135b according to the present embodiment.

The heat exchange fins 135a are disposed between two adjacent refrigerant tubes 130a of the plurality of refrigerant tubes 130 a. The heat exchange fin 135b is disposed between two adjacent cooling water tubes 130b among the plurality of cooling water tubes 130 b.

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

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

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

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

(refrigeration mode)

First, the cooling mode will be described with reference to fig. 6. In the cooling mode (i.e., the first mode), the electronic control unit 32 closes the open/ close valves 38a and 38c, respectively, and opens the open/ close valves 38b and 38d, respectively.

Further, the electronic control device 32 controls the expansion valve 20a to adjust the flow path 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 between the refrigerant outlet of the air/refrigerant heat exchanger 16A and the refrigerant outlet of the indoor condenser 12, and closes the bypass refrigerant passage 18. The electronic control device 32 controls the blower fan 16C to generate an air flow through the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B.

Then, the electronic control unit 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Accordingly, the high-pressure refrigerant discharged from the compressor 10 passes through the indoor condenser 12.

In this case, the air mix door 5 is in a state of closing the air inlet of the indoor condenser 12 and opening the bypass passage 3. Therefore, the cool air from the carburetor 20 is blown out into the vehicle interior through the bypass passage 3.

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

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

The pressure of the evaporated refrigerant is adjusted by a pressure adjusting valve 28. The pressure-adjusted refrigerant flows into the accumulator 26.

On the other hand, the remaining refrigerant, excluding the refrigerant flowing to the expansion valve 20a, of the high-pressure refrigerant having passed through the air/refrigerant heat exchanger 16A flows to the expansion valve 20 b. The refrigerant flowing through the expansion valve 20b is decompressed.

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

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

The refrigerant from the air/refrigerant heat exchanger 16A flows in the order of the expansion valve 20b → the chiller 24 → the accumulator 26.

In the cooling water circuit 50, the cooling water flowing out of the pump 36a flows into the chiller 24. In the chiller 24, the refrigerant absorbs heat from the cooling water. The cooling water having absorbed heat flows through the opening/closing valve 38b 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, the cooling water receives heat released from the secondary battery 44a in the heat exchanger 44 b. The cooling water having radiated heat from the secondary battery 44a flows into the pump 36a through the opening/closing valve 38 d.

Therefore, the cooling water flows in the order of the pump 36a → the chiller 24 → the on-off valve 38b → the heat exchanger 44b → the on-off valve 38d → the pump 36 a. That is, the cooling water circulates between the chiller 24 and the heat exchanger 44 b. 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 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 to close between the cooling water outlet of the pump 36B and the cooling water inlet/outlet 70 of the heat exchanger 44B of the battery unit 44.

Therefore, in the cooling water circuit 52, the cooling water flowing out of 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 the 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 radiates heat to the air flow blown by the blower 16C through the heat exchange fins 135B.

The cooling water having radiated heat 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 the plurality of semiconductor elements.

The cooling water having passed through the cooler 48a flows to the cooler 46a of the motor generator 46. In the cooler 46a, the cooling water receives heat from the electric motor for running. The cooling water having passed through the cooler 46a flows to the pump 36 b.

In this way, the cooling water from the pump 36B flows in the order of the air/cooling water heat exchanger 16B → the cooler 48a → the cooler 46a → the pump 36B, and the heat generated in the inverter 48 and the motor generator 46 is released from the air/cooling water heat exchanger 16B to the air flow.

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 radiates heat to the air flow through the plurality of heat exchange fins 135 a.

For example, in the case where the amount of heat to be radiated from the high-pressure refrigerant to the air flow in the air/refrigerant heat exchanger 16A (i.e., the cooling load) is large and the amount of heat to be radiated from the cooling water in the air/cooling water heat exchanger 16B (i.e., the cooling load) is small at the time of temperature reduction in summer or the like, the following is made.

That is, in the air-refrigerant heat exchanger 16A, heat from the high-pressure refrigerant is released from the refrigerant tubes 130a to the air flow through the plurality of heat exchange fins 135 a.

Further, heat from the high-pressure refrigerant is released from the refrigerant tubes 130a of the air/refrigerant heat exchanger 16A to the air flow through the plurality of heat exchange fins 135a, the connecting portion 135c, and the heat exchange fins 135B of the air/cooling water heat exchanger 16B.

As a result, 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, 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. 7. In the heating mode (i.e., the second mode), the electronic control device 32 opens the open/ close valves 38a and 38c, respectively, as shown in fig. 7. 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, and opens the bypass refrigerant passage 18. The electronic control device 32 controls the blower fan 16C to generate an air flow through the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B.

Then, the electronic control unit 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Accordingly, 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 and closes the bypass passage 3. Therefore, the cool air from the vaporizer 20 flows toward the indoor condenser 12.

Therefore, in the indoor condenser 12, the high-pressure refrigerant radiates heat to the air flow. Thereby, warm air is blown from the indoor condenser 12 into the vehicle interior.

On the other hand, the refrigerant having passed through the indoor condenser 12 passes through the three-way valve 14 and the bypass refrigerant passage 18, and flows into the expansion valves 20a and 20 b. That is, the refrigerant having 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 decompressed by the expansion valve 20 a. The refrigerant decompressed by the expansion valve 20a flows into the evaporator 20. In the evaporator 20, the refrigerant is sucked in from the air flow blown by the blower 4 and evaporated.

The pressure of the evaporated refrigerant is adjusted by a pressure adjusting valve 28. The pressure-adjusted refrigerant flows into the accumulator 26.

On the other hand, the remaining refrigerant other than the refrigerant flowing to the expansion valve 20a, out of the high-pressure refrigerant having passed through the three-way valve 14 and the bypass refrigerant passage 18, flows to the expansion valve 20 b. The refrigerant flowing through the expansion valve 20b is decompressed.

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

Thus, the refrigerant flows in the order of the compressor 10 → the indoor condenser 12 → the three-way valve 14 → the bypass refrigerant passage 18 → the expansion valve 20a → the evaporator 20 → the pressure regulating valve 28 → the accumulator 26 → the compressor 10. The refrigerant from the air/refrigerant heat exchanger 16A flows in the order of the expansion valve 20b → the chiller 24 → the 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 to open between the cooling water outlet of the pump 36B and the cooling water inlet/outlet 70 of the heat exchanger 44B of the battery unit 44.

In the cooling water circuit 51, the cooling water flowing out of 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 36 b.

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

As a result, the secondary battery 44a is heated by heat generated in the motor for running and the plurality of semiconductor elements. Therefore, the output voltage of the secondary battery 44a can be increased in the extremely cold state. Further, the electronic control device 32 stops the electric heater 42.

In the cooling water circuit 53, the cooling water flowing out of the pump 36a flows to the chiller 24. In the chiller 24, the refrigerant absorbs heat from the cooling water. The cooling water having absorbed heat passes through the opening/closing valve 38a and then 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 having absorbed heat from the air flow flows into the pump 36a through the opening/closing valve 38 c. Therefore, the cooling water flows in the order of the pump 36a → the chiller 24 → the open/close valve 38a → the air/cooling water heat exchanger 16B → the open/close valve 38c → the pump 36 a.

Thus, in the air/cooling water heat exchanger 16B, the cooling water radiates 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 tubes 130B.

Also, 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 as described above. Therefore, the refrigerant does not flow through the refrigerant pipe 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 tubes 130 b. 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 unit 32 determines whether or not the cooling water temperature is equal to or higher than a threshold value based on detection signals of the cooling water temperature sensors 50b and 50 c. When the cooling water temperature is less than the threshold value, the electronic control device 32 closes the open- close valves 38b, 38 d.

On the other hand, when the cooling water temperature is equal to or higher than the threshold value, the electronic control unit 32 opens the on-off valves 38b, 38 d. Accordingly, the surplus of the cooling water from the pump 36b, excluding the cooling water flowing through the heat exchanger 44b of the battery unit 44, flows in the order of the on-off valve 38d → the pump 36a → the chiller 24 → the on-off valve 38b → the cooler 48a of the inverter 48.

As a result, a part of the heat generated in the motor generator 46 and the inverter 48 is radiated to the battery unit 44. The remaining heat, excluding the heat radiated to the battery unit 44, of the heat generated by the motor generator 46 and the inverter 48 is radiated from the chiller 24 to the refrigerant.

In this way, the electronic control unit 32 intermittently opens the on-off valves 38b and 38d in response to determination as to whether or not the coolant temperature is equal to or higher than the threshold value. Therefore, the heat generated by the motor generator 46 and the inverter 48 is intermittently transferred to the refrigerant through the chiller 24. Thus, the temperature of the cooling water flowing through the cooling water circuit 51 can be kept at or 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 flows to the cooler 48a of the inverter 48 in the cooling water circuit 51 as indicated by the broken line arrows.

(Heater mode)

Next, the heater mode will be described with reference to fig. 8. The electronic control unit 32 closes the open/ close valves 38a and 38c, respectively. Further, 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 20 a. The electronic control device 32 controls the expansion valve 20b to adjust the flow passage 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 20 b.

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, and opens the bypass refrigerant passage 18. The electronic control unit 32 stops the blower 16C.

Then, the electronic control device 32 operates the electric heater 42. The electronic control unit 32 controls the compressor 10 to start compression of the refrigerant by the compressor 10. Accordingly, 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 and closes the bypass passage 3. Therefore, the cool air from the vaporizer 20 flows toward the indoor condenser 12.

Thus, in the indoor condenser 12, the air stream receives heat from the high-pressure refrigerant. Thereby, warm air is blown from the indoor condenser 12 into the vehicle interior.

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

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

Thus, the refrigerant flows in the order of the compressor 10 → the indoor condenser 12 → the three-way valve 14 → the expansion valve 20b → the chiller 24 → the accumulator 26. The refrigerant does not flow from the indoor condenser 12 to the evaporator 20 through the expansion valve 20 b.

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 to open between the cooling water outlet of the pump 36B and the cooling water inlet/outlet 70 of the heat exchanger 44B of the battery unit 44.

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

Thereby, the heat generated in 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.

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

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

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

In this way, in the chiller 24, the heat released from the cooling water to the refrigerant and the heat given to the refrigerant from the compressor 10 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 from the compressor 10 are used for heating the air in the vehicle compartment.

(defrosting mode)

Next, the defrosting mode will be described with reference to fig. 9. In the defrosting mode (i.e., the third mode), the electronic control device 32 closes the open/ close valves 38a and 38c, respectively, and opens the open/ close valves 38b and 38d, respectively. Further, 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 20 a.

The electronic control device 32 controls the expansion valve 20b to adjust the flow passage cross-sectional area of the refrigerant passage between the bypass refrigerant passage 18 and the chiller 24. That is, the electronic control unit 32 closes the expansion valve 20a and opens the expansion valve 20 b.

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 to close the bypass refrigerant passage 18. The electronic control unit 32 stops the blower 16C.

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

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

The refrigerant flowing through the expansion valve 20b is decompressed by the expansion valve 20 b. The refrigerant decompressed by the expansion valve 20b flows into the chiller 24. In the chiller 24, the refrigerant absorbs heat from the cooling water and evaporates.

The evaporated refrigerant flows to the accumulator 26. The refrigerant flowing to the accumulator 26 is separated into liquid-phase refrigerant and gas-phase refrigerant, and the gas-phase refrigerant flows into the refrigerant inlet of the compressor 10.

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

In the cooling water circuit 50, the cooling water flowing out of the pump 36a flows into the chiller 24. In the chiller 24, the cooling water absorbs heat from the refrigerant. The cooling water having absorbed heat flows in the order of the opening/closing valve 38b → the heat exchanger 44b → the opening/closing valve 38d → the pump 36 a.

Therefore, in the heat exchanger 44b, the cooling water receives heat generated from the electric heater 42. Therefore, the cooling water heated by 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 that the refrigerant absorbs heat from the cooling water in the chiller 24 and the heat that is the work amount given to the refrigerant from the compressor 10 are transferred to the air/refrigerant heat exchanger 16A.

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

Thus, 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. Further, 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 connection portions 135 c.

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 radiates heat to the air flow through the connection portion 135c and the air/cooling water heat exchanger 16B.

That is, the refrigerant radiates heat to the air flow through the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B. Therefore, the heat radiation efficiency of radiating heat from the refrigerant to the air flow can be improved.

In the heating mode, the cooling water in the air/cooling water heat exchanger 16B absorbs heat from the air flow via the connection 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 heat absorption efficiency of the cooling water to absorb heat from the air flow can be improved.

As described above, the in-vehicle thermal management device 1 can improve the heat exchange efficiency of the outdoor unit 16.

In the heat pump system of patent document 1, when the condenser is configured by a plurality of refrigerant tubes through which the refrigerant passes, a distribution tank that distributes the refrigerant to the plurality of refrigerant tubes, and a recovery tank that recovers the refrigerant that has passed through the plurality of refrigerant tubes, the following problems occur.

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

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

As described above, when the outdoor unit is caused to function as an evaporator during heating, the heat exchange efficiency when the refrigerant absorbs heat from the outside air in the outdoor unit is reduced.

In contrast, in the present embodiment, the refrigerant from the compressor 10 does not flow into the air-refrigerant heat exchanger 16A during heating. Therefore, the air-refrigerant heat exchanger 16A as an outdoor unit does not have the problem of the reduction in heat exchange efficiency.

In the heater mode of the present embodiment, heat generated by the inverter 48, the motor generator 46, and the electric heater 42 and heat given to the refrigerant from the compressor 10 are radiated from the indoor condenser 12 to the air flow.

Therefore, more heat can be released from the indoor condenser 12 to the air flow than in the case where only the heat given to the refrigerant from the compressor 10 is radiated from the indoor condenser 12 to the air flow.

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

Therefore, in the present embodiment, more heat can be given to the heat-exchange core 120c than in the case where only the heat given to the refrigerant from the compressor 10 is given to the heat-exchange core 120 c. Therefore, frost adhering to the heat exchange core 120c can be melted well.

(second embodiment)

In the first embodiment, the example in which the in-vehicle thermal management device 1 includes the on-off valve 38d that opens and closes between the refrigerant outlet of the pump 36b and the refrigerant inlet of the pump 36a is described.

However, instead of this, a second embodiment in which the in-vehicle thermal management device 1 includes the regulator 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. 10.

In fig. 10, the same reference numerals as in fig. 1 denote the same components, and a description thereof will be omitted.

The in-vehicle thermal management device 1 according to the present embodiment uses the regulating valve 38e instead of the opening/closing valve 38d shown in fig. 1.

The regulator 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 36 a; and an electric actuator that drives the valve element. The valve body is controlled by an electronic control unit 32 via an electric actuator.

The electronic control unit 32 controls the regulating valve 38e based on the detection signals of the cooling water temperature sensors 50b and 50c such that the sectional area of the refrigerant flow path increases as the cooling water temperature increases.

On the other hand, the electronic control unit 32 controls the regulating valve 38e based on the detection signals of the cooling water temperature sensors 50b and 50c such that the sectional area of the refrigerant flow path is smaller as the cooling water temperature is lower.

Therefore, in the heating mode, the higher the cooling water temperature is, the more the amount of cooling water that flows from the pump 36b to the chiller 24 through the pump 36a can be increased. The lower the cooling water temperature is, the smaller the amount of cooling water flowing from the pump 36b to the chiller 24 through the pump 36a can be.

As described above, the heat radiated from the chiller 24 to the refrigerant can be increased as the cooling water temperature is higher. Therefore, the temperature of the cooling water flowing through the heat exchanger 44b of the battery unit 44 can be controlled within a predetermined range with high accuracy.

According to the present embodiment described above, in the cooling mode, the in-vehicle thermal management device 1 releases heat to the airflow by the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B, as in the first embodiment described above. In the heating mode, the cooling water absorbs heat from the air flow via the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B.

As described above, similarly to the first embodiment, the in-vehicle thermal management device 1 can be provided that improves the heat exchange efficiency of the outdoor unit 16.

(third embodiment)

In the first embodiment described above, the example in which the air/cooling water heat exchanger 16B is disposed upstream in the air flow direction with respect to the air/refrigerant heat exchanger 16A in the outdoor unit 16 of the in-vehicle thermal management device 1 has been described, but instead of this, a configuration as described below may be employed.

That is, in the third embodiment, as shown in fig. 11, the air/cooling water heat exchanger 16B is disposed 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 provided 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 to spread from the heat exchange fin 135B side of the air/cooling water heat exchanger 16B to the connection portion 135c side.

Thereby, frost is formed thinner in the heat exchange fins 135B than in the case where the connection portion 135c is formed on the leeward side of the air/cooling water heat exchanger 16B. Accordingly, the air flow path formed by the heat exchange fins 135b is prevented from being clogged with frost. Therefore, heat exchange between the air and the cooling water via the heat exchange fins 135b is maintained, and thus the heating performance can be maintained for a long time.

The present embodiment differs from the first embodiment only in the structure of the outdoor unit 16, and the other structures are the same. In fig. 11, the same reference numerals as in fig. 1 denote the same components, and a description thereof will be omitted.

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

As described above, similarly to the first embodiment, the in-vehicle thermal management device 1 can be provided that improves the heat exchange efficiency of the outdoor unit 16.

(fourth embodiment)

In the first embodiment described above, an example in which the in-vehicle thermal management device 1 uses the indoor condenser 12, which radiates heat from the refrigerant to the air flow, as the heating heat exchanger in the indoor air-conditioning casing 2 is described.

However, instead of this, the present fourth embodiment of the heater core 61 that radiates heat to the air flow using warm water in the in-vehicle thermal management device 1 will be described with reference to fig. 12.

As shown in fig. 12, the in-vehicle thermal management device 1 according to the present embodiment includes a hot water circuit 60 including a heater core 61.

The in-vehicle thermal management device 1 of the present embodiment includes a hot water circuit 60 instead of the indoor condenser 12 of fig. 1.

The configuration of the in-vehicle thermal management device 1 according to the present embodiment other than the hot water circuit 60 is the same as that of the in-vehicle thermal management device 1 according to the first embodiment. In fig. 12, the same reference numerals as in fig. 1 denote the same components, and a description thereof will be omitted.

Therefore, the hot water circuit 60 in the in-vehicle thermal management device 1 according to the present embodiment will be mainly described. The hot water circuit 60 includes a heater core 61, a water/refrigerant heat exchanger 62, and a pump 63. The heater core 61, the water/refrigerant heat exchanger 62, and the pump 63 are connected by hot water pipes to form a closed circuit in which hot water circulates. The heater core 61 is disposed in the indoor air conditioning casing 2.

The pump 63 circulates warm water in the order of the pump 63 → the heater core 61 → the water/refrigerant heat exchanger 62 → the pump 63. The heater core 61 radiates heat from the warm water to the cool air passing through the vaporizer 20.

The water/refrigerant heat exchanger 62 is a first radiator that absorbs heat from the refrigerant with the warm water having passed through the heater core 61. The hot water having absorbed heat is sucked into the pump 63. The pump 63 causes warm water to flow toward the water/refrigerant heat exchanger 62.

The water/refrigerant heat exchanger 62 is disposed 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 radiates heat from the high-pressure refrigerant from the compressor 10 to warm water.

Thus, by circulating the warm water between the water/refrigerant heat exchanger 62 and the heater core 61, the warm water having absorbed heat from the high-pressure refrigerant in the water/refrigerant heat exchanger 62 is radiated from the heater core 61 to the cold air.

Therefore, the heater core 61 heats the cool air blown out from the vaporizer 20 with warm water. Thereby, the warm air heated by the heater core 61 is blown into the vehicle interior.

According to the present embodiment described above, in the in-vehicle thermal management device 1, the refrigerant radiates heat to the airflow through the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B in the cooling mode, as in the first embodiment described above. In the heating mode, the cooling water absorbs heat from the air flow via the air/refrigerant heat exchanger 16A and the air/cooling water heat exchanger 16B.

As described above, even in the present embodiment including the hot water circuit 60 instead of the indoor condenser 12, the in-vehicle thermal management device 1 capable of improving the heat exchange efficiency of the outdoor unit 16 can be provided as in the first embodiment.

(fifth embodiment)

In the first embodiment described above, the defrosting mode in which the in-vehicle thermal management device 1 uses the high-pressure refrigerant to melt the frost adhering to the air/cooling water heat exchanger 16B is described.

The fifth embodiment, in which the defrosting mode in which the cooling water melts the frost adhering to the air/cooling water heat exchanger 16B, will be described with reference to fig. 13.

The in-vehicle thermal management device 1 according to the present embodiment has the same configuration as the in-vehicle thermal management device 1 according to the first embodiment. The in-vehicle thermal management device 1 according to the present embodiment differs from the in-vehicle thermal management device 1 according to the above-described embodiment only in the operation in the defrosting mode, and the other operations are the same as each other. Therefore, the defrosting mode of the in-vehicle thermal management device 1 according to the present embodiment will be described.

First, the electronic control unit 32 closes the open/ close valves 38a and 38c, respectively, and opens the open/ close valves 38b and 38d, respectively. Further, 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 20 a.

The electronic control device 32 controls the expansion valve 20b to adjust the flow passage cross-sectional area of the refrigerant passage between the bypass refrigerant passage 18 and the chiller 24. That is, the electronic control unit 32 closes the expansion valve 20a and opens the expansion valve 20 b.

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, and opens the bypass refrigerant passage 18. The electronic control unit 32 stops the blower 16C. The electronic control unit 32 operates the pumps 36a, 36 b.

The electronic control device 32 controls the three-way valve 40 to open 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 to close between the cooling water outlet of the pump 36B and the cooling water inlet/outlet 70 of the heat exchanger 44B of the battery unit 44.

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

Accordingly, 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 cooler 24 → the accumulator 26 → the compressor 10.

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

The cooling water flowing out of the pump 36B flows through the cooling water circuit 52 in the order of the three-way valve 40 → the air/cooling water heat exchanger 16B → the cooler 48a → the cooler 46a → the pump 36B.

Here, in the cooler 48a, the cooling water absorbs heat from the plurality of semiconductor elements. In the cooler 46a, the cooling water absorbs heat from the electric motor for running. 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.

As a result, the heat generated from the inverter 48 and the motor generator 46 is supplied to the air/cooling water heat exchanger 16B via the cooling water. Therefore, the frost adhering to the air/cooling water heat exchanger 16B can be melted by the heat from the cooling water.

According to the present embodiment described above, in the cooling mode, the air/refrigerant heat exchanger 16A radiates heat from the refrigerant by 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, heat generated from the inverter 48 and the motor generator 46 is supplied 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 favorably melted.

(other embodiments)

(1) In the first to fifth embodiments, the vehicle thermal management device 1 in which the thermal management device according to the present invention is applied to an automobile has been described, but instead, the thermal management device according to the present invention may be applied to a mobile body such as a train or an airplane other than an automobile. Alternatively, the thermal management device of the present invention may be applied to an installation type air conditioner for a house, a building, or the like.

(2) In the above embodiment, an example in which the heat of the refrigerant flowing through the air/refrigerant heat exchanger 16A is used to defrost in the defrosting mode is described. In the fifth embodiment, an example in which defrosting is performed by the heat of the cooling water as the defrosting mode is described.

Further, a defrosting mode in which the defrosting mode of the first embodiment and the defrosting mode of the fifth embodiment are combined may be implemented. That is, the following defrosting mode may be implemented: the defrosting is performed by the heat of the refrigerant, and the defrosting is performed by the heat of the cooling water.

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

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

Alternatively, the air/refrigerant heat exchanger 16A may be disposed on the upstream side of the air flow with respect to the air/cooling water heat exchanger 16B, and defrosting may be performed by the heat of the cooling water as a defrosting mode, as in the fifth embodiment.

Alternatively, in a state where the air/refrigerant heat exchanger 16A is disposed on the upstream side of the air flow with respect to the air/cooling water heat exchanger 16B, a defrosting mode may be performed in which defrosting is performed by the heat of the refrigerant and the heat of the cooling water, as in the above-described (2).

(5) In the first to fifth embodiments, the description has been given of the example in which the high-pressure refrigerant discharged from the compressor 10 is caused to flow through the indoor condenser 12 in the cooling mode. Alternatively, the high-pressure refrigerant discharged from the compressor 10 may be caused to flow into the air/refrigerant heat exchanger 16A while bypassing the indoor condenser 12.

(6) In the first to fifth embodiments, the example in which the refrigerant is caused to flow through the evaporator 20 in the heating mode has been described, but instead, the refrigerant may be prevented from flowing to the evaporator 20 in the heating mode.

(7) In the first to fifth embodiments, the description has been given of an example using the cooling water circuit 52 for radiating heat generated in the motor generator 46 and the inverter 48 from the air/cooling water heat exchanger 16B to the airflow. However, instead of this, the cooling water circuit 52 may be eliminated.

(8) The present invention is not limited to the above-described embodiments, and can be modified as appropriate. The above embodiments are not necessarily unrelated to each other, and may be appropriately combined except for a case where it is obviously impossible to combine them. It is needless to say that in each of the above embodiments, elements constituting the embodiments are not necessarily essential except for cases where they are specifically indicated to be essential and cases where they are apparently considered to be essential in principle. In the above embodiments, when numerical values such as the number, numerical value, amount, and range of the constituent elements of the embodiments are mentioned, the number is not limited to a specific number unless otherwise stated explicitly or clearly in principle. In the above embodiments, the shapes, positional relationships, and the like of the constituent elements are not limited to the shapes, positional relationships, and the like, unless otherwise stated explicitly or the principle is limited to a specific shape, positional relationship, and the like.

In the first to fifth embodiments and other embodiments described above, the heat management device includes the blower that generates the air flow passing through the radiator and the second radiator. In the first mode, the second radiator radiates heat from the refrigerant to the air flow via the radiator in a state where the blower generates the air flow.

In the second mode, the heat medium of the radiator absorbs heat from the air flow via the second radiator in a state where the blower generates the air flow. In the third mode, the second radiator radiates heat from the refrigerant to the radiator in a state where the blower stops the generation of the air flow.

The heat management device further includes an on-off valve that opens and closes a space between the cooler and the radiator in the first heat medium circuit.

In the first mode, the second radiator radiates heat from the refrigerant to the air flow via the radiator in a state where the opening and closing valve closes between the cooler and the radiator. In the third mode, the second radiator radiates heat from the refrigerant to the radiator in a state where the opening and closing valve is open between the cooler and the radiator.

(conclusion)

According to a first aspect described in part or all of the first to fifth embodiments and other embodiments, the heat management device includes: a compressor that sucks, compresses, and discharges a refrigerant; and a first radiator that radiates heat from the refrigerant discharged from the compressor.

The heat management device is provided with: a second radiator that radiates heat to the air flow from the refrigerant having passed through the first radiator; a first pressure reducing valve and a second pressure reducing valve that reduce the pressure of the refrigerant after passing through the first radiator; and an evaporator that evaporates the refrigerant having passed through the first pressure reducing valve.

The heat management device is provided with: a chiller that evaporates the refrigerant having passed through the second pressure reducing valve by absorbing heat from the heat medium; and a bypass refrigerant passage for bypassing the refrigerant having passed through the first radiator to the first pressure reducing valve and the second pressure reducing valve and flowing the refrigerant to the second radiator.

The heat management device is provided with: and a switching valve set to any one of a first state and a second state. The first state is a form that opens between the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator, and closes the bypass refrigerant passage. The second state is a state in which a refrigerant outlet of the first radiator and a refrigerant inlet of the second radiator are closed, and the bypass refrigerant passage is opened.

The heat management device is provided with: a radiator that exchanges heat between the thermal medium and the air flow; and a heat medium circuit for circulating a heat medium between the refrigerator and the radiator.

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

According to a second aspect, the thermal management device is provided with a connecting portion for connecting the second heat sink and the radiator.

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

In a second mode in which the heat medium in the heat medium circuit circulates in a state in which the switching valve is 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 a third aspect, a thermal management device includes: a heat generating body that radiates heat to the heat medium; and a second heat medium circuit for circulating the heat medium between the heat generating body and the radiator when the heat medium circuit is used as the first heat medium circuit.

In the first mode, the radiator radiates heat to the air flow in a state where the heat medium is circulated in the second heat medium circuit.

According to a fourth aspect, a thermal management device includes: a second heating element that radiates heat to the heat medium when the heating element is used as the first heating element; and a third heat medium circuit for circulating the heat medium between the second heat generating body and the refrigerator.

This allows the heat generated by the second heat generating element to be transferred to the refrigerant via the cooler.

According to a fifth aspect, the radiator of the thermal management device is arranged outdoors.

In a third mode in which the heat medium is circulated in the third heat medium circuit with the switching valve set to the first state and the second heat generating element dissipating heat to the heat medium, the heat supplied from the second heat generating element to the heat medium is transferred to the refrigerant via the chiller. The refrigerant in the second radiator radiates heat to the radiator through the connection portion to melt frost attached to the radiator.

This enables the heat generated by the second heat-generating body to be used for defrosting the radiator.

According to a sixth aspect, the second heat sink is arranged on an upstream side of the air flow with respect to the radiator.

According to a seventh aspect, the second heat sink includes: a condensing unit that condenses the refrigerant by radiating heat from the refrigerant to the heat medium; a gas-liquid separation unit that separates the refrigerant having passed through the condensation unit into a liquid-phase refrigerant and a gas-phase refrigerant, and discharges the liquid-phase refrigerant; and a supercooling unit that supercools the liquid-phase refrigerant discharged from the gas-liquid separation unit.

According to an eighth aspect, in the second mode, the first radiator radiates heat from the refrigerant, and in the first mode, the second radiator radiates heat from the refrigerant to the air flow.

Claims (8)

1. A thermal management device is characterized by comprising:

a compressor (10) that sucks, compresses, and discharges a refrigerant;

a first radiator (12) that radiates heat from the refrigerant discharged from the compressor;

a second radiator (16A) that radiates heat to an air flow from the refrigerant that has passed through the first radiator;

a first pressure reducing valve (20a) and a second pressure reducing valve (20b) that reduce the pressure of the refrigerant after passing through the first radiator;

an evaporator (20) that evaporates the refrigerant having passed through the first pressure reducing valve;

a chiller (24) that evaporates the refrigerant having passed through the second pressure reducing valve by absorbing heat from a heat medium;

a bypass refrigerant passage (18) through which the refrigerant having passed through the first radiator bypasses the second radiator and flows to the first pressure reducing valve and the second pressure reducing valve;

a switching valve (14) that is set to any one of a first state that opens between a refrigerant outlet of the first radiator and a refrigerant inlet of the second radiator and closes the bypass refrigerant passage, and a second state that closes between the refrigerant outlet of the first radiator and the refrigerant inlet of the second radiator and opens the bypass refrigerant passage;

a radiator (16B) that exchanges heat between the thermal medium and the air flow; and

a heat medium circuit (53) for circulating the heat medium between the refrigerator and the radiator,

in a first mode in which the switching valve is set to the first state, the refrigerant in the second radiator radiates heat to the airflow via the radiator,

in a second mode in which the heat medium in the heat medium circuit circulates in a state in which the switching valve is set to the second state, the heat medium in the radiator absorbs heat from the airflow via the second radiator.

2. The thermal management device of claim 1,

a connecting part (135c) for connecting the second heat sink and the radiator,

in a first mode in which the switching valve is set to the first state, the refrigerant in the second radiator radiates heat to the airflow via the connecting portion and the radiator,

in a second mode in which the heat medium in the heat medium circuit circulates in a state in which the switching valve is set to the second state, the heat medium in the radiator absorbs heat from the airflow via the connecting portion and the second radiator.

3. The heat management device according to claim 1 or 2, comprising:

heating elements (48, 46) that radiate heat to the heat medium; and

a second heat medium circuit (52) for circulating the heat medium between the heat generating body and the radiator when the heat medium circuit is used as the first heat medium circuit,

in the first mode, the radiator radiates heat to the air flow in a state where the heat medium is circulated in the second heat medium circuit.

4. The heat management device according to claim 3, comprising:

a second heating element (42) that, when the heating element is used as the first heating element, radiates heat to the heat medium; and

and a third heat medium circuit (50) for circulating the heat medium between the second heat-generating body and the chiller.

5. The thermal management device of claim 4,

the radiator is arranged outdoors,

in a third mode in which the heat medium circulates in the third heat medium circuit in a state in which the switching valve is set to the first state and the second heat generating element radiates heat to the heat medium, the heat given to the heat medium from the second heat generating element is moved to the refrigerant via the chiller,

the refrigerant in the second radiator radiates heat to the radiator to melt frost attached to the radiator.

6. The thermal management device of claim 4,

the second radiator is disposed on an upstream side of the air flow with respect to the radiator.

7. The thermal management device according to any of claims 1 to 5,

the second heat sink includes:

a condensing unit (100) that condenses the refrigerant by radiating heat from the refrigerant to the heat medium;

a gas-liquid separation unit (120) that separates the refrigerant that has passed through the condensation unit into a liquid-phase refrigerant and a gas-phase refrigerant, and discharges the liquid-phase refrigerant; and

and an supercooling unit (110) that supercools the liquid-phase refrigerant discharged from the gas-liquid separation unit.

8. The thermal management device according to any of claims 1 to 7,

in the second mode, causing the first heat sink to dissipate heat from the refrigerant,

in the first mode, the second radiator is caused to radiate heat from the refrigerant to the airflow.

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