Temperature control device

Abstract

To provide a temperature regulation device having a simple structure which can cool an object to be subject to temperature regulation by using a refrigeration cycle for air conditioning.SOLUTION: A refrigeration cycle 12 has a compressor 13, a refrigerant heat radiator 14, a first expansion valve 16, a first evaporator 17, a second expansion valve 20, and a second evaporator 21. In a heat medium circuit 30, a heat medium circulates flowing through an air heat exchanger 32 and the second evaporator 21. The refrigerant heat radiator 14 radiates heat from the refrigerant to outdoor air. The first evaporator 17 causes the refrigerant and front ventilation air Af to exchange heat to evaporate the refrigerant and cool the front ventilation air Af. The second evaporator 21 causes the refrigerant and the heat medium in the heat medium circuit 30 to exchange heat to evaporate the refrigerant and cool the heat medium. The air heat exchanger 32 causes the heat medium and rear ventilation air Ab to be subject to temperature regulation to exchange heat to cool the rear ventilation air Ab.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a temperature control device for regulating the temperature of a temperature control target.

Background Art

[0002] Patent Document 1 describes a vapor compression refrigeration cycle. The evaporator included in the refrigeration cycle cools the blown air sent into the passenger compartment space.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In recent years, in vehicles such as electric vehicles, the number of temperature control targets to be cooled or heated has tended to increase. Therefore, it is an urgent task to provide a temperature control device for regulating the temperature of the temperature control target with a simple configuration.

[0005] Therefore, the inventors focused on the fact that an air-conditioning refrigeration cycle as shown in Patent Document 1 has already been installed in many vehicles. Then, the inventors considered simplifying the configuration of the temperature control device by using the air-conditioning refrigeration cycle. As a result of the inventors' detailed examination, the above has been found.

[0006] In view of the above points, an object of the present invention is to provide a temperature control device with a simple configuration capable of cooling or heating a temperature control target by using an air-conditioning refrigeration cycle.

Means for Solving the Problems

[0007] To achieve the above object, the temperature control device according to claim 1 is A temperature control device for controlling the temperature of temperature control targets (74, Ab, Ac), a compressor (13) for compressing a refrigerant, a refrigerant radiator for dissipating heat from the refrigerant flowing out of the compressor (4 2), a first expansion valve (16) for decompressing the refrigerant flowing out of the refrigerant radiator, a first evaporator (17) for evaporating the refrigerant flowing out of the first expansion valve and then flowing it to the compressor, a second expansion valve (20) for decompressing the refrigerant flowing out of the refrigerant radiator, and a second evaporator (21) for evaporating the refrigerant flowing out of the second expansion valve and then flowing it to the compressor, and a refrigeration cycle (12); It has a first heat exchanger (48, 51), a heat medium radiator (49), and a flow rate adjustment mechanism (50), and a first heat medium circuit (46) in which a first heat medium circulates while flowing through at least one of the first heat exchanger and the heat medium radiator and a refrigerant radiator, Second having heat exchange parts (32, 33), Second a heat medium Second circulates while flowing through the heat exchange part and the second evaporator Second and a heat medium circuit (30), The first evaporator evaporates the refrigerant by heat-exchanging the refrigerant with the blown air (Af) sent to the air-conditioned target space (71a) and cools the blown air, The second evaporator Second evaporates the refrigerant by heat-exchanging the heat medium with the refrigerant and Second cools the heat medium, Second The heat exchange part cools the temperature control target by heat-exchanging the temperature control target with Second the heat medium and the flow rate adjustment mechanism adjusts the flow rate ratio between the flow rate of the first heat medium flowing through the first heat exchanger and the flow rate of the first heat medium flowing through the heat medium radiator, the refrigerant radiator heats the first heat medium by exchanging heat between the first heat medium and the refrigerant, the heat medium radiator dissipates heat from the first heat medium, the first heat exchanger heats the temperature control target by exchanging heat between the temperature control target and the first heat medium, the refrigeration cycle is configured to be able to block the flow of refrigerant from the refrigerant radiator to the second evaporator, when the flow rate adjustment mechanism causes the first heat medium to flow to the first heat exchanger, in the refrigeration cycle, while the refrigerant flows from the refrigerant radiator to the first evaporator, the flow of the refrigerant from the refrigerant radiator to the second evaporator is blocked, when the refrigerant in the refrigeration cycle flows from the refrigerant radiator to the second evaporator, the flow rate adjustment mechanism causes the first heat medium to flow to the heat medium radiator while blocking the flow of the first heat medium to the first heat exchanger.

[0008] In this way, it is possible to cool the temperature control target using a refrigeration cycle for cooling the blown air. In other words, it is possible to equip the refrigeration cycle for cooling the blown air with the function of cooling the temperature control target.

[0009] And since heat is transferred by the heat medium between the heat exchange section and the second evaporator, it is possible to avoid the situation where the arrangement of the second evaporator is restricted because the second evaporator has a function of cooling the temperature control target. For example, it is possible to avoid a situation where it is necessary to lengthen the refrigerant piping of the refrigeration cycle because the second evaporator has a function of cooling the temperature control target. Therefore, regardless of the arrangement of the heat exchange section, for example, the refrigeration cycle can be configured compactly, so that the temperature control device can have a simple configuration.

[0013] The reference numerals in parentheses attached to each component etc. indicate an example of the correspondence relationship between the component etc. and the specific components etc. described in the embodiments described later.

Brief Description of the Drawings

[0014]

Figure 1

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Embodiments for Carrying out the Invention

[0015] Hereinafter, each embodiment will be described with reference to the drawings. In each of the following embodiments, parts that are identical or equivalent to each other are denoted by the same reference numerals in the figures.

[0016] (First Embodiment) As shown in FIGS. 1 and 2, the temperature control device 10 of the present embodiment is mounted on a vehicle 70. The vehicle 70 is, for example, a hybrid vehicle.

[0017] Note that the arrows at both ends of FIG. 2 respectively indicate the directions of the vehicle 70 shown in that FIG. 2. That is, in FIG. 2, the vehicle front-rear direction D1, which is the front-rear direction of the vehicle 70, and the vehicle up-down direction D2, which is the up-down direction of the vehicle 70, are indicated by the arrows at both ends. These directions D1 and D2 are directions that intersect each other, and strictly speaking, directions that are perpendicular to each other. Also, in the description of the present embodiment, the front in the vehicle front-rear direction D1 is also referred to as the vehicle front, the rear in the vehicle front-rear direction D1 is also referred to as the vehicle rear, the upper side in the vehicle up-down direction D2 is also referred to as the vehicle upper side, and the lower side in the vehicle up-down direction D2 is also referred to as the vehicle lower side.

[0018] As shown in FIG. 2, inside the vehicle 70, a passenger compartment space 71 is formed in which a seat 72 for passengers is arranged, separated from the outside of the vehicle 70. The passenger compartment space 71 includes a front passenger compartment 71a and a rear passenger compartment 71b. The front passenger compartment 71a and the rear passenger compartment 71b each occupy a part of the passenger compartment space 71 and are different spaces from each other. The passenger compartment space 71 may also be referred to as the "inside of the vehicle compartment".

[0019] The front passenger compartment 71a is located in the front of the vehicle in the passenger compartment space 71, and the front seat 721 of the seats 72 for passengers is arranged in the front passenger compartment 71a. The rear passenger compartment 71b is located in the rear of the vehicle in the passenger compartment space 71, and the rear seat 722 of the seats 72 for passengers is arranged in the rear passenger compartment 71b.

[0020] As shown in FIGS. 1 and 2, the temperature control device 10 is a device for adjusting the temperature of the air Af (that is, the front blowing air Af) sent to the front passenger compartment 71a of the vehicle 70 and the temperature of the air Ab (that is, the rear blowing air Ab) sent to the rear passenger compartment 71b of the vehicle 70, respectively. In the vehicle 70 of the present embodiment, the front passenger compartment 71a and the rear passenger compartment 71b of the vehicle 70 are air-conditioned separately.

[0021] Specifically, the temperature control device 10 of the present embodiment has a function of cooling the forward blowing air Af and a function of cooling the rearward blowing air Ab, respectively. In the present embodiment, the forward passenger compartment 71a corresponds to the air-conditioning target space of the present disclosure, the rearward passenger compartment 71b corresponds to the temperature control space of the present disclosure, the forward blowing air Af corresponds to the blowing air of the present disclosure, and the rearward blowing air Ab corresponds to the temperature control target of the present disclosure.

[0022] As shown in FIGS. 1 to 3, the temperature control device 10 includes a refrigeration cycle 12, a heat medium circuit 30, and a circuit control unit 80 that controls the refrigeration cycle 12 and the heat medium circuit 30.

[0023] The refrigeration cycle 12 is configured as a vapor compression refrigeration cycle. Further, the refrigeration cycle 12 is operated as a subcritical refrigeration cycle in which the refrigerant pressure on the high-pressure side in the cycle does not exceed the critical pressure of the refrigerant.

[0024] The refrigeration cycle 12 is a refrigerant circuit through which the refrigerant circulates, and the refrigerant is enclosed in the refrigerant circuit as the refrigeration cycle 12. As the refrigerant circulating in the refrigeration cycle 12, various refrigerants can be adopted. In the present embodiment, for example, a chlorofluorocarbon refrigerant such as HFO134a is adopted.

[0025] The refrigeration cycle 12 has a compressor 13, a refrigerant radiator 14, a first expansion valve 16, a first evaporator 17, a second expansion valve 20, a second evaporator 21, and pipes connecting them.

[0026] In the refrigeration cycle 12, the discharge port 13a of the compressor 13 is connected to the refrigerant inlet 14a of the refrigerant radiator 14, and the refrigerant outlet 14b of the refrigerant radiator 14 is connected to the refrigerant inlet 16a of the first expansion valve 16 and the refrigerant inlet 20a of the second expansion valve 20. Further, the refrigerant outlet 16b of the first expansion valve 16 is connected to the refrigerant inlet 17a of the first evaporator 17, and the refrigerant outlet 20b of the second expansion valve 20 is connected to the refrigerant inlet 21a of the second evaporator 21. Also, the refrigerant outlet 17b of the first evaporator 17 and the refrigerant outlet 21b of the second evaporator 21 are both connected to the suction port 13b of the compressor 13.

[0027] The compressor 13 has a discharge port 13a and a suction port 13b, compresses the refrigerant inhaled from the suction port 13b, and discharges the compressed refrigerant from the discharge port 13a. Specifically, the compressor 13 is an electric compressor, and has a compression mechanism that compresses the refrigerant introduced into the compression chamber and an electric motor that rotationally drives the compression mechanism.

[0028] The compressor 13 is controlled by a control signal output from the circuit control unit 80. For example, the on / off of the compressor 13 and the rotation speed of the compressor 13 (specifically, the rotation speed of the electric motor of the compressor 13) are controlled by the control signal output from the circuit control unit 80.

[0029] The refrigerant radiator 14 has a refrigerant inlet 14a into which the refrigerant flows and a refrigerant outlet 14b from which the refrigerant flows out. The high-temperature and high-pressure refrigerant discharged from the compressor 13 flows into the refrigerant inlet 14a of the refrigerant radiator 14.

[0030] The refrigerant radiator 14 is a heat exchanger that exchanges heat between the refrigerant and the outside air and dissipates heat from the refrigerant to the outside air by this heat exchange. Specifically, the refrigerant radiator 14 is a condenser (in other words, a capacitor), and by the heat exchange between the refrigerant and the outside air, heat is dissipated from the refrigerant to the outside air and the refrigerant is condensed. The refrigerant that has dissipated heat and condensed in the refrigerant radiator 14 flows out from the refrigerant outlet 14b and flows to the first expansion valve 16 and the second expansion valve 20.

[0031] Further, the refrigerant radiator 14 is disposed in the front of the vehicle 70 so that outside air as traveling wind hits it, for example, when the vehicle is traveling. The outside air is supplied to the refrigerant radiator 14 by the vehicle traveling or by the operation of a blower (not shown). Note that the outside air is the air outside the vehicle or the air in a space open to the outside of the vehicle.

[0032] The first expansion valve 16 has a refrigerant inlet 16a into which the refrigerant flows and a refrigerant outlet 16b from which the refrigerant flows out. The first expansion valve 16 is a pressure reducing device that reduces the pressure of the refrigerant flowing into the refrigerant inlet 16a of the first expansion valve 16. The first expansion valve 16 causes the pressure-reduced refrigerant to flow out from the refrigerant outlet 16b.

[0033] The first expansion valve 16 is an electric expansion valve and has a valve body and an electric actuator. The electric actuator of the first expansion valve 16 is configured to include, for example, a stepping motor, and changes the throttle opening degree of the first expansion valve 16 by displacing the valve body. Since the electric actuator of the first expansion valve 16 is controlled by a control signal from the circuit control unit 80, the throttle opening degree of the first expansion valve 16 is increased or decreased according to the control signal from the circuit control unit 80.

[0034] Also, the first expansion valve 16 is configured such that its throttle opening degree can be set to zero, that is, the first expansion valve 16 can be fully closed. When the first expansion valve 16 is fully closed, the flow of the refrigerant from the refrigerant radiator 14 to the first evaporator 17 is blocked. When the first expansion valve 16 is open, the refrigerant decompressed by the first expansion valve 16 flows out from the refrigerant outlet 16b of the first expansion valve 16 and flows to the refrigerant inlet 17a of the first evaporator 17. Therefore, the refrigeration cycle 12 is configured to be able to block the flow of the refrigerant from the refrigerant radiator 14 to the first evaporator 17 by including the first expansion valve 16 that can be fully closed.

[0035] The first evaporator 17 has a refrigerant inlet 17a into which the refrigerant flows and a refrigerant outlet 17b from which the refrigerant flows out. The first evaporator 17 is a heat exchanger for cooling the forward blowing air Af sent to the forward passenger compartment 71a, and is disposed in an air conditioning unit (not shown). The air conditioning unit is disposed, for example, inside an instrument panel provided in the front of the vehicle in the forward passenger compartment 71a. The forward blowing air Af is blown by a blower (not shown) of the air conditioning unit, for example.

[0036] For example, the first evaporator 17 is configured such that a plurality of tubes through which the refrigerant flows and a plurality of corrugated fins are arranged alternately, and in the first evaporator 17, the air that exchanges heat with the refrigerant passes between the tubes.

[0037] Specifically, the first evaporator 17 is disposed in an air passage formed within the air conditioning unit through which the forward blowing air Af flows. The first evaporator 17 causes the refrigerant flowing into the refrigerant inlet 17a to exchange heat with the forward blowing air Af passing through the first evaporator 17. Through this heat exchange, the refrigerant is evaporated and the forward blowing air Af is cooled. The refrigerant evaporated and absorbing heat in the first evaporator 17 flows out from the refrigerant outlet 17b and flows to the suction port 13b of the compressor 13. That is, the first evaporator 17 evaporates the refrigerant decompressed by the first expansion valve 16 and flowing out from the first expansion valve 16 and then flows it to the suction port 13b of the compressor 13.

[0038] The second expansion valve 20 has a refrigerant inlet 20a into which the refrigerant flows and a refrigerant outlet 20b from which the refrigerant flows out. The second expansion valve 20 decompresses the refrigerant flowing into the refrigerant inlet 20a of the second expansion valve 20 and causes the decompressed refrigerant to flow out from the refrigerant outlet 20b. The refrigerant flowing out from the refrigerant outlet 20b of the second expansion valve 20 flows to the refrigerant inlet 21a of the second evaporator 21.

[0039] The second expansion valve 20 is disposed at a location different from the first expansion valve 16, but has the same configuration as the first expansion valve 16. That is, the second expansion valve 20 has a valve body and an electric actuator, and the throttle opening degree of the second expansion valve 20 is increased or decreased according to a control signal from the circuit control unit 80. And the second expansion valve 20 is configured to be able to fully close the second expansion valve 20.

[0040] When the second expansion valve 20 is fully closed, the flow of the refrigerant from the refrigerant radiator 14 to the second evaporator 21 is blocked. When the second expansion valve 20 is open, the refrigerant decompressed by the second expansion valve 20 flows out from the refrigerant outlet 20b of the second expansion valve 20 and flows to the refrigerant inlet 21a of the second evaporator 21. Therefore, the refrigeration cycle 12 is configured to be able to block the flow of the refrigerant from the refrigerant radiator 14 to the second evaporator 21 by including the second expansion valve 20 that can be fully closed.

[0041] Since the first expansion valve 16 and the second expansion valve 20 can each be fully closed in this way, they include a function as a refrigerant flow path switching unit that selectively switches the refrigerant flow path to, for example, a first flow state, a second flow state, and a third flow state. In the first flow state, the flow of refrigerant from the refrigerant radiator 14 to the first evaporator 17 via the first expansion valve 16 is blocked, and the flow of refrigerant from the refrigerant radiator 14 to the second evaporator 21 via the second expansion valve 20 is allowed. Also, in the second flow state, the flow of refrigerant from the refrigerant radiator 14 to the first evaporator 17 via the first expansion valve 16 is allowed, and the flow of refrigerant from the refrigerant radiator 14 to the second evaporator 21 via the second expansion valve 20 is blocked. Further, in the third flow state, both the flow of refrigerant from the refrigerant radiator 14 to the first evaporator 17 via the first expansion valve 16 and the flow of refrigerant from the refrigerant radiator 14 to the second evaporator 21 via the second expansion valve 20 are allowed.

[0042] The second evaporator 21 has a refrigerant inlet 21a through which refrigerant flows in, a refrigerant outlet 21b through which refrigerant flows out, a heat medium inlet 21c through which the heat medium of the heat medium circuit 30 flows in, and a heat medium outlet 21d through which the heat medium flows out. The second evaporator 21 is a heat exchanger (in other words, a chiller) that exchanges heat between the refrigerant and the heat medium of the heat medium circuit 30. By exchanging heat between the refrigerant and the heat medium, heat is absorbed by the refrigerant to evaporate the refrigerant and the heat medium is cooled.

[0043] The refrigerant that has absorbed heat in the second evaporator 21 flows out from the refrigerant outlet 21b and flows to the suction port 13b of the compressor 13. At the same time, the heat medium cooled in the second evaporator 21 flows out from the heat medium outlet 21d. That is, the second evaporator 21 evaporates the refrigerant that has been depressurized by the second expansion valve 20 and flows out from the second expansion valve 20 and then flows to the suction port 13b of the compressor 13, and causes the heat medium cooled along with the evaporation of the refrigerant to flow out from the heat medium outlet 21d.

[0044] In the refrigeration cycle 12 with the configuration as described above, when the compressor 13 is operating, if the first expansion valve 16 is open and the second expansion valve 20 is fully closed, the refrigerant flows into the first evaporator 17 but does not flow into the second evaporator 21. Conversely, if the first expansion valve 16 is fully closed and the second expansion valve 20 is open, the refrigerant does not flow into the first evaporator 17 but flows into the second evaporator 21. Also, if both the first expansion valve 16 and the second expansion valve 20 are open, the refrigerant flows into both the first evaporator 17 and the second evaporator 21. Thus, in the refrigeration cycle 12, when the compressor 13 is operating, the refrigerant evaporates in one or both of the first evaporator 17 and the second evaporator 21 and circulates while releasing heat in the refrigerant radiator 14.

[0045] The heat medium circuit 30 includes a pump 31, an air heat exchanger 32 as a heat exchange section, and piping connecting them. The heat medium circuit 30 is a fluid circuit in which the heat medium circulates while flowing through the pump 31, the air heat exchanger 32, and the second evaporator 21. The heat medium circulating in the heat medium circuit 30 is, for example, a liquid, and as the heat medium, an antifreeze such as a solution containing ethylene glycol can be adopted.

[0046] In the heat medium circuit 30, the discharge port 31a of the pump 31 is connected to the heat medium inlet 21c of the second evaporator 21, and the heat medium outlet 21d of the second evaporator 21 is connected to the heat medium inlet 32a of the air heat exchanger 32. Also, the heat medium outlet 32b of the air heat exchanger 32 is connected to the suction port 31b of the pump 31. Therefore, in the heat medium circuit 30, when the pump 31 operates, the heat medium discharged from the discharge port 31a of the pump 31 flows through the second evaporator 21 and the air heat exchanger 32 in that order and is then sucked into the suction port 31b of the pump 31.

[0047] The pump 31 is an electric pump that pumps the heat medium. The pump 31 has a discharge port 31a and a suction port 31b. The pump 31 sucks the heat medium inhaled from the suction port 31b and discharges it from the discharge port 31a, thereby circulating the heat medium in the heat medium circuit 30.

[0048] The on / off operation of the pump 31 and the rotational speed of the pump 31 are controlled according to a control signal output from the circuit control unit 80. For example, the discharge flow rate of the pump 31 increases as the rotational speed of the pump 31 increases. That is, the pump 31 can increase or decrease the discharge flow rate of the pump 31.

[0049] The air heat exchanger 32 has a heat medium inlet 32a through which the heat medium flows and a heat medium outlet 32b from which the heat medium flows out. The air heat exchanger 32 is a heat exchanger for cooling the rear blowing air Ab sent to the rear passenger compartment 71b. The rear blowing air Ab is blown by a blower (not shown), for example.

[0050] For example, the air heat exchanger 32 is configured by alternately arranging a plurality of tubes through which the heat medium flows and a plurality of corrugated fins. In the air heat exchanger 32, the air that exchanges heat with the heat medium passes between the tubes.

[0051] Specifically, the air heat exchanger 32 is disposed in an air passage through which the rear blowing air Ab flows toward the rear passenger compartment 71b. Then, the air heat exchanger 32 exchanges heat between the heat medium that has flowed into the heat medium inlet 32a and the rear blowing air Ab that passes through the air heat exchanger 32, absorbs heat from the heat medium by this heat exchange, and cools the rear blowing air Ab. The heat medium that has absorbed heat in the air heat exchanger 32 flows out from the heat medium outlet 32b and flows to the suction port 31b of the pump 31.

[0052] The circuit control unit 80 shown in FIG. 3 is an electronic control device composed of a computer including a semiconductor memory as a non-transitory tangible recording medium and a processor and its peripheral circuits. The circuit control unit 80 executes a computer program stored in the semiconductor memory. By executing this computer program, a method corresponding to the computer program is executed. That is, the circuit control unit 80 executes various control processes according to the computer program.

[0053] On the output side of the circuit control unit 80, a plurality of controlled devices in the temperature control device 10 that are controlled by the circuit control unit 80 are connected. Specifically, on the output side of the circuit control unit 80, a compressor 13 of the refrigeration cycle 12, a first expansion valve 16, a second expansion valve 20, a pump 31 of the heat medium circuit 30, etc. are connected.

[0054] On the input side of the circuit control unit 80, in addition to a plurality of sensors included in the refrigeration cycle 12 or the heat medium circuit 30, an operation panel 82 operated by the occupant is connected. The operation panel 82 is arranged in the passenger compartment space 71 as an operating device used for various input operations by the occupant. For example, the operation panel 82 is arranged near the instrument panel in the passenger compartment space 71 and has various operation switches operated by the occupant. Operation signals from the various operation switches included in the operation panel 82 are input to the circuit control unit 80.

[0055] The temperature control device 10 of this embodiment is configured as described above. For example, when the rear blowing air Ab is cooled by the temperature control device 10, the compressor 13 of the refrigeration cycle 12 and the pump 31 of the heat medium circuit 30 are operated. Then, the second expansion valve 20 is set to a state where the refrigerant can flow, and the throttle opening degree of the second expansion valve 20 is adjusted so that the second expansion valve 20 exhibits a pressure reducing action.

[0056] Thereby, in the refrigeration cycle 12, the refrigerant circulating in the refrigeration cycle 12 evaporates in the second evaporator 21 and absorbs heat from the heat medium in the heat medium circuit 30, condenses in the refrigerant radiator 14 and dissipates heat to the outside air. And in the heat medium circuit 30, the heat medium circulating in the heat medium circuit 30 absorbs heat from the rear blowing air Ab in the air heat exchanger 32 and dissipates heat to the refrigerant of the refrigeration cycle 12 in the second evaporator 21. In this way, the rear blowing air Ab is cooled.

[0057] At this time, the front blowing air Af may or may not be cooled by the temperature control device 10. For example, when the front blowing air Af is not cooled by the temperature control device 10, the first expansion valve 16 is fully closed.

[0058] On the other hand, when the forward blowing air Af is also cooled by the temperature control device 10 together with the rearward blowing air Ab, the first expansion valve 16 is also put into a state where the refrigerant can flow, and the throttle opening degree of the first expansion valve 16 is adjusted so that the first expansion valve 16 exerts a pressure reducing action. Thereby, the refrigerant in the refrigeration cycle 12 evaporates in the first evaporator 17 and absorbs heat from the forward blowing air Af. Then, the refrigerant flowing out from the first evaporator 17 and the refrigerant flowing out from the second evaporator 21 are both sucked into the suction port 13b of the compressor 13. In this way, the forward blowing air Af is also cooled.

[0059] When the forward blowing air Af is cooled by the temperature control device 10 while the rearward blowing air Ab is not cooled, the compressor 13 of the refrigeration cycle 12 is operated and the pump 31 of the heat medium circuit 30 is stopped. Then, the first expansion valve 16 is put into a state where the refrigerant can flow, and the throttle opening degree of the first expansion valve 16 is adjusted so that the first expansion valve 16 exerts a pressure reducing action. On the other hand, the second expansion valve 20 is fully closed.

[0060] Thereby, in the refrigeration cycle 12, the refrigerant circulating in the refrigeration cycle 12 evaporates in the first evaporator 17 and absorbs heat from the forward blowing air Af, condenses in the refrigerant radiator 14, and dissipates heat to the outside air. In this way, the forward blowing air Af is cooled.

[0061] As described above, according to the present embodiment, the refrigeration cycle 12 includes a compressor 13, a refrigerant radiator 14, a first expansion valve 16, a first evaporator 17, a second expansion valve 20, and a second evaporator 21. In the heat medium circuit 30, the heat medium circulates while flowing through the air heat exchanger 32 and the second evaporator 21. The refrigerant radiator 14 dissipates heat from the refrigerant to the outside air. The first evaporator 17 evaporates the refrigerant and cools the forward blowing air Af by exchanging heat between the refrigerant and the forward blowing air Af. The second evaporator 21 evaporates the refrigerant and cools the heat medium by exchanging heat between the refrigerant and the heat medium of the heat medium circuit 30. Then, the air heat exchanger 32 cools the rearward blowing air Ab by exchanging heat between the heat medium and the rearward blowing air Ab.

[0062] Therefore, it is possible to cool the rear blowing air Ab to be temperature-controlled by using the refrigeration cycle 12 for cooling the front blowing air Af. In other words, it is possible to make the refrigeration cycle 12 for cooling the front blowing air Af also have the function of cooling the rear blowing air Ab.

[0063] And, since heat is transferred by the heat medium between the air heat exchanger 32 in contact with the rear blowing air Ab and the second evaporator 21, it is possible to avoid the situation that the arrangement of the second evaporator 21 is restricted because the second evaporator 21 has the function of cooling the rear blowing air Ab. For example, it is possible to avoid a situation where it is necessary to lengthen the refrigerant piping of the refrigeration cycle 12 because the second evaporator 21 has the function of cooling the rear blowing air Ab. Therefore, regardless of the arrangement of the air heat exchanger 32, for example, the refrigeration cycle 12 can be configured compactly, so that the temperature control device 10 can be configured simply.

[0064] For example, if the refrigeration cycle 12 is configured compactly and the refrigerant piping of the refrigeration cycle 12 is shortened as a whole, it is possible to avoid the complication of the control of the refrigeration cycle 12 caused by the long refrigerant piping.

[0065] (1) Also, according to the present embodiment, the heat medium circuit 30 has a pump 31 that circulates the heat medium in the heat medium circuit 30 and can increase or decrease the flow rate of the heat medium. Therefore, it is possible to freely adjust the flow rate of the heat medium flowing through the second evaporator 21 according to the amount of heat absorbed by the refrigerant from the heat medium in the second evaporator 21.

[0066] (2) Also, according to the present embodiment, the rear passenger compartment 71b as the temperature-controlled space where the rear blowing air Ab cooled by the air heat exchanger 32 goes is a space that occupies a part of the passenger compartment space 71. Therefore, the air heat exchanger 32 can be provided at a position relatively close to the component devices of the refrigeration cycle 12 (for example, the first and second evaporators 17, 21, etc.). Thereby, for example, the piping of the heat medium circuit 30 can be configured short.

[0067] (Second Embodiment) Next, the second embodiment will be described. In this embodiment, the differences from the above-described first embodiment will be mainly described. Also, the same or equivalent parts as those in the above-described embodiment will be omitted or simplified in the description. This also applies to the description of the embodiments described later.

[0068] As shown in FIGS. 4 and 5, the heat medium circuit 30 of the present embodiment has a heat exchange plate 33 as a heat exchange part in place of the air heat exchanger 32 (see FIG. 1) of the first embodiment.

[0069] The heat exchange plate 33 is made of, for example, a metal plate material with high thermal conductivity, and cools the temperature control object 74 by heat conduction between the heat exchange plate 33 and the temperature control object 74 in contact with the heat exchange plate 33. The heat exchange plate 33 is provided, for example, in a cup holder inner space 75a as a temperature control chamber formed in a cup holder 75 provided in the passenger compartment space 71. And the heat exchange plate 33 is arrange | positioned at the bottom part of the cup holder inner space 75a, and cools the drink cup etc. which are the temperature control object 74 placed on the heat exchange plate 33. In the present embodiment, the temperature control object 74 corresponds to the temperature control object of the present disclosure.

[0070] Specifically, an internal flow path through which the heat medium flows is formed inside the heat exchange plate 33, and the heat exchange plate 33 has a heat medium inlet 33a for allowing the heat medium to flow into the internal flow path and a heat medium outlet 33b for allowing the heat medium to flow out from the internal flow path. Then, when the heat medium flows through the internal flow path of the heat exchange plate 33 and the temperature control object 74 comes into contact with the heat exchange plate 33, heat exchange is performed between the heat medium and the temperature control object 74.

[0071] In the present embodiment, the heat medium inlet 33a of the heat exchange plate 33 is connected to the heat medium outlet 21d of the second evaporator 21, and the heat medium outlet 33b of the heat exchange plate 33 is connected to the suction port 31b of the pump 31. Therefore, in the heat medium circuit 30, when the pump 31 operates, the heat medium discharged from the discharge port 31a of the pump 31 flows in the order of the second evaporator 21 and the heat exchange plate 33 and is then sucked into the suction port 31b of the pump 31.

[0072] As described above, according to this embodiment, the heat medium circuit 30 has the heat exchange plate 33. And the heat exchange plate 33 exchanges heat between the object 74 to be temperature-controlled that contacts the heat exchange plate 33 and the heat medium flowing in the heat exchange plate 33 by heat conduction, thereby cooling the object 74 to be temperature-controlled. Therefore, it is possible to cool the object 74 to be temperature-controlled by heat conduction without the need for blowing air.

[0073] Except for what has been described above, this embodiment is the same as the first embodiment. And in this embodiment, the effects achieved by the configuration common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment.

[0074] (Third Embodiment) Next, the third embodiment will be described. In this embodiment, the points different from the aforementioned first embodiment will be mainly described.

[0075] As shown in FIG. 6, in this embodiment, the refrigeration cycle 12 has a pressure regulating valve 23. In this regard, this embodiment is different from the first embodiment.

[0076] Specifically, the pressure regulating valve 23 has a refrigerant inlet 23a into which the refrigerant flows and a refrigerant outlet 23b from which the refrigerant flows out. And the pressure regulating valve 23 is provided on the downstream side of the refrigerant flow in the first evaporator 17 and on the upstream side of the refrigerant flow in the compressor 13. That is, the refrigerant outlet 17b of the first evaporator 17 is connected to the refrigerant inlet 23a of the pressure regulating valve 23, and the refrigerant outlet 23b of the pressure regulating valve 23 is connected to the suction port 13b of the compressor 13.

[0077] The pressure regulating valve 23 is a valve device also called an evaporation pressure regulating valve, and has a function of adjusting the refrigerant evaporation pressure in the first evaporator 17 to be equal to or higher than a reference pressure capable of suppressing frosting in order to suppress frosting of the first evaporator 17. In other words, the pressure regulating valve 23 maintains the refrigerant evaporation pressure in the first evaporator 17 at a predetermined value or higher, which is the reference pressure.

[0078] Specifically, when the pressure of the refrigerant in the first evaporator 17 drops below the reference pressure, the pressure regulating valve 23 reduces the throttle opening degree (i.e., the cross-sectional area of the refrigerant passage), and when the pressure of the refrigerant exceeds the reference pressure, the throttle opening degree is increased. Thus, the pressure regulating valve 23 maintains the refrigerant evaporation temperature in the first evaporator 17 at or above the frost suppression temperature (e.g., 1°C) capable of suppressing frosting in the first evaporator 17. For example, the pressure regulating valve 23 is a mechanical variable throttle mechanism that increases the valve opening degree as the pressure of the refrigerant on the outlet side of the first evaporator 17 rises. Note that the refrigerant flow rate through the first evaporator 17 increases or decreases according to the throttle opening degree of the pressure regulating valve 23. Therefore, the pressure regulating valve 23 also functions as a flow rate regulating valve.

[0079] Also, in the present embodiment, the temperature control target cooled by the air heat exchanger 32 is not the rearward blowing air Ab (see FIG. 1), but the refrigerating air blown into a refrigerating chamber in which, for example, food and drink are stored. The refrigerating chamber corresponds to a temperature control space provided inside the vehicle 70 and separated from the outside of the vehicle 70.

[0080] (1) As described above, according to the present embodiment, the refrigeration cycle 12 has the pressure regulating valve 23. The pressure regulating valve 23 is provided on the downstream side of the refrigerant flow in the first evaporator 17 and on the upstream side of the refrigerant flow in the compressor 13, and maintains the refrigerant evaporation pressure in the first evaporator 17 at a predetermined value or more. Therefore, while maintaining the temperature of the passenger compartment space 71 at an appropriate temperature, for example, it is possible to lower the temperature of the refrigerating chamber into which the air cooled by the air heat exchanger 32 flows below the temperature of the passenger compartment space 71.

[0081] Except for what has been described above, the present embodiment is the same as the first embodiment. And in the present embodiment, the effects achieved by the configuration common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment.

[0082] Note that although the present embodiment is a modification based on the first embodiment, it is also possible to combine the present embodiment with the aforementioned second embodiment.

[0083] (Fourth Embodiment) Next, the fourth embodiment will be described. In this embodiment, the differences from the aforementioned first embodiment will be mainly described.

[0084] As shown in FIG. 7, in this embodiment, the heat medium circuit 30 has a battery heat exchanger 34. In this regard, this embodiment is different from the first embodiment.

[0085] Specifically, in the heat medium circuit 30 of this embodiment, the heat medium outlet 21d of the second evaporator 21 is connected to the heat medium inlet 32a of the air heat exchanger 32 and the heat medium inlet 34a of the battery heat exchanger 34, respectively. And the suction port 31b of the pump 31 is connected to the heat medium outlet 32b of the air heat exchanger 32 and the heat medium outlet 34b of the battery heat exchanger 34, respectively.

[0086] The battery heat exchanger 34 is a heat exchanger for cooling the battery 76. The battery 76 functions as a power source for the driving motor of the vehicle 70. This battery 76 is a secondary battery that can be repeatedly charged and discharged, and is composed of, for example, a lithium ion battery or a nickel metal hydride battery. And in order for the battery 76 to exhibit appropriate charge and discharge performance, the temperature of the battery 76 is preferably maintained within a predetermined temperature range, and the battery 76 generates heat during its charge and discharge.

[0087] The battery heat exchanger 34 has a heat medium inlet 34a through which the heat medium flows in and a heat medium outlet 34b through which the heat medium flows out. The battery heat exchanger 34 exchanges heat between the heat medium flowing into the battery heat exchanger 34 from the heat medium inlet 34a and the battery 76, thereby cooling the battery 76. The heat medium after exchanging heat with the battery 76 flows out from the heat medium outlet 34b and is sucked into the suction port 31b of the pump 31. For example, the battery heat exchanger 34 is integrally formed with the battery 76 and is configured to be able to cool the battery 76 while equalizing the temperatures of a plurality of battery cells included in the battery 76.

[0088] In the heat medium circuit 30 configured as described above, when the pump 31 operates, the heat medium discharged from the discharge port 31a of the pump 31 flows to the second evaporator 21, and from the second evaporator 21, it flows in parallel to the air heat exchanger 32 and the battery heat exchanger 34. Then, the heat medium is sucked from the air heat exchanger 32 into the suction port 31b of the pump 31 and is also sucked from the battery heat exchanger 34 into the suction port 31b of the pump 31.

[0089] Therefore, when the pump 31 operates and the heat medium cooled by the second evaporator 21 flows out from the second evaporator 21, the cooled heat medium flows to the air heat exchanger 32 and the battery heat exchanger 34 respectively. Therefore, when the rearward blowing air Ab (see FIG. 2) is cooled by the air heat exchanger 32, at the same time, the battery 76 is cooled by the heat medium in the battery heat exchanger 34.

[0090] (1) As described above, according to the present embodiment, the heat medium circuit 30 has the battery heat exchanger 34, and the battery heat exchanger 34 exchanges heat between the battery 76 and the heat medium. Therefore, it is also possible to cool the battery 76 by using the heat medium circuit 30 that cools the rearward blowing air Ab.

[0091] Except for what has been described above, the present embodiment is the same as the first embodiment. And in the present embodiment, the effects obtained from the configurations common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment.

[0092] Note that although the present embodiment is a modification based on the first embodiment, it is also possible to combine the present embodiment with the aforementioned second embodiment or third embodiment.

[0093] (Fifth Embodiment) Next, the fifth embodiment will be described. In the present embodiment, the points different from the aforementioned first embodiment will be mainly described.

[0094] As shown in FIG. 8, the temperature control device 10 of the present embodiment includes a fluid circuit 36 for cooling the battery. The refrigeration cycle 12 of the present embodiment has a third expansion valve 24 and a third evaporator 25, and the fluid circuit 36 has a battery heat exchanger 34. In these respects, the present embodiment is different from the first embodiment.

[0095] Specifically, in the refrigeration cycle 12 of the present embodiment, the refrigerant outlet 14b of the refrigerant radiator 14 is connected to the refrigerant inlet 16a of the first expansion valve 16, the refrigerant inlet 20a of the second expansion valve 20, and the refrigerant inlet 24a of the third expansion valve 24. Further, the refrigerant outlet 24b of the third expansion valve 24 is connected to the refrigerant inlet 25a of the third evaporator 25. Further, the suction port 13b of the compressor 13 is connected to the refrigerant outlet 17b of the first evaporator 17, the refrigerant outlet 21b of the second evaporator 21, and the refrigerant outlet 25b of the third evaporator 25.

[0096] The third expansion valve 24 has a refrigerant inlet 24a into which the refrigerant flows and a refrigerant outlet 24b from which the refrigerant flows out. The third expansion valve 24 reduces the pressure of the refrigerant flowing from the refrigerant radiator 14 into the refrigerant inlet 24a of the third expansion valve 24, and allows the decompressed refrigerant to flow out from the refrigerant outlet 24b. The refrigerant flowing out from the refrigerant outlet 24b of the third expansion valve 24 flows to the refrigerant inlet 25a of the third evaporator 25.

[0097] The third expansion valve 24 is arranged at a different position from the first expansion valve 16, but has the same configuration as the first expansion valve 16. That is, the third expansion valve 24 has a valve body and an electric actuator, and the throttle opening degree of the third expansion valve 24 is increased or decreased according to a control signal from the circuit control unit 80 (see FIG. 3). And the third expansion valve 24 is configured to be able to fully close the third expansion valve 24.

[0098] When the third expansion valve 24 is fully closed, the flow of the refrigerant from the refrigerant radiator 14 to the third evaporator 25 is blocked. When the third expansion valve 24 is open, the refrigerant decompressed by the third expansion valve 24 flows out from the refrigerant outlet 24b of the third expansion valve 24 and flows to the refrigerant inlet 25a of the third evaporator 25.

[0099] Since the third expansion valve 24 can also be fully closed in this way, in the present embodiment, the first expansion valve 16, the second expansion valve 20, and the third expansion valve 24 function as a refrigerant flow path switching unit that switches the refrigerant flow path of the refrigeration cycle 12.

[0100] The third evaporator 25 has a refrigerant inlet 25a into which the refrigerant flows, a refrigerant outlet 25b from which the refrigerant flows out, a fluid inlet 25c into which the fluid for battery cooling in the fluid circuit 36 flows, and a fluid outlet 25d from which the fluid for battery cooling flows out. The third evaporator 25 is arranged at a location different from the second evaporator 21, but has the same configuration as the second evaporator 21.

[0101] That is, the third evaporator 25 is a heat exchanger (in other words, a chiller) that exchanges heat between the refrigerant and the fluid for battery cooling. Then, the third evaporator 25 absorbs heat from the fluid for battery cooling to the refrigerant through the heat exchange between the refrigerant and the fluid for battery cooling, thereby evaporating the refrigerant and cooling the fluid for battery cooling.

[0102] The refrigerant that has absorbed heat in the third evaporator 25 flows out from the refrigerant outlet 25b and flows to the suction port 13b of the compressor 13. At the same time, the fluid for battery cooling that has been cooled in the third evaporator 25 flows out from the fluid outlet 25d. That is, the third evaporator 25 evaporates the refrigerant that has been depressurized by the third expansion valve 24 and flows out from the third expansion valve 24 and then flows to the suction port 13b of the compressor 13, and causes the fluid for battery cooling that has been cooled along with the evaporation of the refrigerant to flow out from the fluid outlet 25d.

[0103] In the refrigeration cycle 12 with the configuration described above, when the compressor 13 is operating, if the third expansion valve 24 is open, the refrigerant is depressurized by the third expansion valve 24 and then flows to the third evaporator 25. On the other hand, if the third expansion valve 24 is fully closed, the refrigerant does not flow to the third evaporator 25. Thus, in the refrigeration cycle 12, when the compressor 13 is operating, the refrigerant circulates while evaporating in any one or all of the first to third evaporators 17, 21, 25 and radiating heat in the refrigerant radiator 14.

[0104] The fluid circuit 36 for battery cooling includes a battery cooling pump 37, a battery heat exchanger 34, and piping connecting them. In the fluid circuit 36, the battery cooling fluid circulates while flowing through the battery cooling pump 37, the battery heat exchanger 34, and the third evaporator 25. The battery cooling fluid may be the same fluid as the heat medium in the heat medium circuit 30 or various fluids different from the heat medium. However, in this embodiment, the same fluid as the heat medium in the heat medium circuit 30 (specifically, the same liquid as the heat medium) is adopted as the battery cooling fluid.

[0105] In this embodiment, the battery heat exchanger 34 is included in the fluid circuit 36, and in the fluid circuit 36, the battery cooling fluid circulates. Therefore, the heat medium inlet 34a of the battery heat exchanger 34 is referred to as the fluid inlet 34a, and the heat medium outlet 34b of the battery heat exchanger 34 is referred to as the fluid outlet 34b.

[0106] In the fluid circuit 36, the discharge port 37a of the battery cooling pump 37 is connected to the fluid inlet 25c of the third evaporator 25, and the fluid outlet 25d of the third evaporator 25 is connected to the fluid inlet 34a of the battery heat exchanger 34. Also, the fluid outlet 34b of the battery heat exchanger 34 is connected to the suction port 37b of the battery cooling pump 37. Therefore, in the fluid circuit 36, when the battery cooling pump 37 operates, the battery cooling fluid discharged from the discharge port 37a of the battery cooling pump 37 flows through the third evaporator 25 and the battery heat exchanger 34 in this order and is then sucked into the suction port 37b of the battery cooling pump 37.

[0107] The battery cooling pump 37 is an electric pump that pumps the battery cooling fluid. The battery cooling pump 37 has a discharge port 37a and a suction port 37b, and discharges the battery cooling fluid inhaled from the suction port 37b from the discharge port 37a. The on / off of the battery cooling pump 37 and the rotation speed of the battery cooling pump 37 are controlled according to a control signal output from the circuit control unit 80. For example, the discharge flow rate of the battery cooling pump 37 increases as the rotation speed of the battery cooling pump 37 increases.

[0108] The battery heat exchanger 34 of the present embodiment is the same as the battery heat exchanger 34 of the fourth embodiment, except that it is provided in the fluid circuit 36. Therefore, the battery heat exchanger 34 of the present embodiment exchanges heat between the battery cooling fluid flowing into the battery heat exchanger 34 from the fluid inlet 34a and the battery 76, thereby cooling the battery 76.

[0109] In the present embodiment, for example, the operation of the temperature control device 10 when the rearward blowing air Ab is cooled and the operation of the temperature control device 10 when the forward blowing air Af is cooled are the same as those in the first embodiment.

[0110] Also, when the battery 76 is cooled by the temperature control device 10 of the present embodiment, the compressor 13 of the refrigeration cycle 12 and the battery cooling pump 37 of the fluid circuit 36 are operated. Then, the third expansion valve 24 is set in a state where the refrigerant can flow, and the throttle opening degree of the third expansion valve 24 is adjusted so that the third expansion valve 24 exhibits a pressure-reducing action.

[0111] As a result, in the refrigeration cycle 12, the refrigerant circulating in the refrigeration cycle 12 evaporates in the third evaporator 25 and absorbs heat from the battery cooling fluid in the fluid circuit 36, condenses in the refrigerant radiator 14, and dissipates heat to the outside air. And in the fluid circuit 36, the battery cooling fluid absorbs heat from the battery 76 in the battery heat exchanger 34 and dissipates heat to the refrigerant of the refrigeration cycle 12 in the third evaporator 25. In this way, the battery 76 is cooled.

[0112] At this time, if necessary, the first expansion valve 16 and the second expansion valve 20 of the refrigeration cycle 12 may be fully closed respectively, or may be set in a state where the refrigerant can flow.

[0113] On the other hand, when the battery 76 is not cooled while the compressor 13 of the refrigeration cycle 12 is operating, the third expansion valve 24 is fully closed and the battery cooling pump 37 is stopped.

[0114] (1) As described above, according to the present embodiment, in the fluid circuit 36, the fluid for battery cooling circulates while flowing through the battery cooling pump 37, the battery heat exchanger 34, and the third evaporator 25 of the refrigeration cycle 12. The third evaporator 25 evaporates the refrigerant and cools the fluid for battery cooling by exchanging heat between the fluid for battery cooling and the refrigerant. Then, the battery heat exchanger 34 of the fluid circuit 36 exchanges heat between the battery 76 and the fluid for battery cooling. Therefore, it is possible to make the temperature of the heat medium cooled by the second evaporator 21 of the refrigeration cycle 12 different from the temperature of the fluid for battery cooling cooled by the third evaporator 25.

[0115] Except for what has been described above, the present embodiment is the same as the first embodiment. And in the present embodiment, the effects achieved by the configuration common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment.

[0116] Note that although the present embodiment is a modification based on the first embodiment, it is also possible to combine the present embodiment with the aforementioned second embodiment or third embodiment.

[0117] (Sixth Embodiment) Next, the sixth embodiment will be described. In the present embodiment, the points different from the aforementioned first embodiment will be mainly described.

[0118] As shown in FIGS. 9 and 10, the temperature control device 10 of the present embodiment has a function of cooling the forward blowing air Af, but does not have a function of cooling the rearward blowing air Ab. Instead, the temperature control device 10 of the present embodiment has a function of warming the temperature control target air Ac, which is the air sent to the temperature control space 77. In the present embodiment, the temperature control target air Ac corresponds to the temperature control target of the present disclosure.

[0119] The temperature-controlled space 77 of the present embodiment is, for example, the internal space of a storage compartment where the temperature inside the space is maintained and small items, food and drink, etc. are stored. It is separated from the outside of the vehicle 70 (see FIG. 2) and provided inside the vehicle 70. Specifically, the temperature-controlled space 77, which is the space inside the storage compartment, is provided, for example, so as to occupy a part of the passenger compartment space 71, or is provided adjacent to the passenger compartment space 71 at a predetermined location around the passenger compartment space 71.

[0120] The temperature control device 10 of the present embodiment includes a refrigeration cycle 12, a heat medium circuit 46 that replaces the heat medium circuit 30 of the first embodiment, and a circuit control unit 80 that controls the refrigeration cycle 12 and the heat medium circuit 46. The circuit control unit 80 of the present embodiment is the same as the circuit control unit 80 of the first embodiment, except that the objects to be controlled are the refrigeration cycle 12 and the heat medium circuit 46.

[0121] The refrigeration cycle 12 of the present embodiment has a compressor 13, a refrigerant radiator 42 that replaces the refrigerant radiator 14 of the first embodiment, an expansion valve 16, an evaporator 17, and pipes connecting them. And the refrigeration cycle 12 of the present embodiment does not have the second expansion valve 20 (see FIG. 1) and the second evaporator 21 of the first embodiment.

[0122] In the present embodiment, since the second expansion valve 20 is not provided, the first expansion valve 16 is simply referred to as the expansion valve 16. Also, in the present embodiment, since the second evaporator 21 is not provided, the first evaporator 17 is simply referred to as the evaporator 17.

[0123] In the refrigeration cycle 12, the discharge port 13a of the compressor 13 is connected to the refrigerant inlet 42a of the refrigerant radiator 42, and the refrigerant outlet 42b of the refrigerant radiator 42 is connected to the refrigerant inlet 16a of the expansion valve 16. Also, the refrigerant outlet 16b of the expansion valve 16 is connected to the refrigerant inlet 17a of the evaporator 17, and the refrigerant outlet 17b of the evaporator 17 is connected to the suction port 13b of the compressor 13. Therefore, the refrigerant discharged from the discharge port 13a of the compressor 13 flows through the refrigerant radiator 42, the expansion valve 16, and the evaporator 17 in that order and is sucked into the suction port 13b of the compressor 13.

[0124] The compressor 13 of the present embodiment is the same as the compressor 13 of the first embodiment.

[0125] The refrigerant radiator 42 has a refrigerant inlet 42a into which the refrigerant flows, a refrigerant outlet 42b from which the refrigerant flows out, a heat medium inlet 42c into which the heat medium of the heat medium circuit 46 flows, and a heat medium outlet 42d from which the heat medium flows out. The high-temperature and high-pressure refrigerant discharged from the compressor 13 flows into the refrigerant inlet 42a of the refrigerant radiator 42.

[0126] The refrigerant radiator 42 is a heat exchanger that exchanges heat between the refrigerant and the heat medium of the heat medium circuit 46, and dissipates heat from the refrigerant to the heat medium by this heat exchange to heat the heat medium. Specifically, the refrigerant radiator 42 is a condenser (in other words, a water-cooled condenser), and by the heat exchange between the refrigerant and the heat medium, heat is dissipated from the refrigerant to the heat medium and the refrigerant is condensed. The refrigerant that has been radiated and condensed in the refrigerant radiator 42 flows out from the refrigerant outlet 42b and flows to the expansion valve 16.

[0127] The expansion valve 16 of the present embodiment may have a configuration that can be fully closed in the same manner as the first expansion valve 16 of the first embodiment, but in the present embodiment, it does not have a configuration that allows the expansion valve 16 to be fully closed. Except for this, the expansion valve 16 of the present embodiment is the same as the first expansion valve 16 of the first embodiment.

[0128] The evaporator 17 of the present embodiment is the same as the first evaporator 17 of the first embodiment.

[0129] In the refrigeration cycle 12 of the present embodiment with the above-described configuration, when the compressor 13 is operating, the refrigerant discharged from the compressor 13 circulates in the order of the refrigerant radiator 42, the expansion valve 16, and the evaporator 17 and returns to the compressor 13. And the refrigerant circulates while dissipating heat in the refrigerant radiator 42 and evaporating in the evaporator 17.

[0130] Except for what has been described above, the refrigeration cycle 12 of the present embodiment is the same as the refrigeration cycle 12 of the first embodiment.

[0131] The heat medium circuit 46 is a fluid circuit in which the heat medium circulates while flowing through the refrigerant radiator 42. The heat medium of the heat medium circuit 46 in the present embodiment may be various fluids different from the heat medium of the heat medium circuit 30 in the first embodiment, but the same fluid as the heat medium in the first embodiment is adopted as the heat medium in the present embodiment. Therefore, the heat medium of the heat medium circuit 46 in the present embodiment is also a liquid.

[0132] The heat medium circuit 46 includes a pump 47, an air heat exchanger 48 as a heat exchange section, a heat medium radiator 49, a flow rate adjustment mechanism 50, and piping connecting them. In the heat medium circuit 46, the discharge port 31a of the pump 31 is connected to the heat medium inlet 48a of the air heat exchanger 48 and the heat medium inlet 49a of the heat medium radiator 49. Further, the heat medium outlet 48b of the air heat exchanger 48 is connected to the first inlet port 50a of the flow rate adjustment mechanism 50, and the heat medium outlet 49b of the heat medium radiator 49 is connected to the second inlet port 50b of the flow rate adjustment mechanism 50. Further, the outlet port 50c of the flow rate adjustment mechanism 50 is connected to the heat medium inlet 42c of the refrigerant radiator 42, and the heat medium outlet 42d of the refrigerant radiator 42 is connected to the suction port 47b of the pump 47.

[0133] Therefore, in the heat medium circuit 46, when the pump 47 operates, the heat medium discharged from the discharge port 47a of the pump 47 flows to the air heat exchanger 48 or the heat medium radiator 49 according to the switching state of the flow rate adjustment mechanism 50. Then, the heat medium flows from the air heat exchanger 48 or the heat medium radiator 49, in the order of the flow rate adjustment mechanism 50 and the refrigerant radiator 42, and is sucked from the refrigerant radiator 42 into the suction port 47b of the pump 47.

[0134] The pump 47 in the present embodiment is the same as the pump 31 in the first embodiment. Therefore, the pump 47 in the present embodiment has a discharge port 47a and a suction port 47b. Then, the pump 47 discharges the heat medium sucked from the suction port 47b from the discharge port 47a, thereby circulating the heat medium in the heat medium circuit 46. For example, the discharge flow rate of the pump 47 increases as the rotation speed of the pump 47 increases. That is, the pump 47 can increase or decrease the discharge flow rate of the pump 47.

[0135] The air heat exchanger 48 of this embodiment is a heat exchanger having a plurality of tubes and a plurality of corrugated fins, similar to the air heat exchanger 32 of the first embodiment, for example. The air heat exchanger 48 has a heat medium inlet 48a into which the heat medium flows and a heat medium outlet 48b from which the heat medium flows out. And the air heat exchanger 48 is a heating heat exchanger that heats the temperature-controlled air Ac sent to the temperature-controlled space 77. The temperature-controlled air Ac is blown, for example, by a blower (not shown).

[0136] Specifically, the air heat exchanger 48 is disposed in an air passage through which the temperature-controlled air Ac flows toward the temperature-controlled space 77. And the air heat exchanger 48 exchanges heat between the heat medium flowing into the heat medium inlet 48a and the temperature-controlled air Ac passing through the air heat exchanger 48, and by this heat exchange, heat is radiated from the heat medium to the temperature-controlled air Ac to heat the temperature-controlled air Ac. The heat medium that has radiated heat in the air heat exchanger 48 flows out from the heat medium outlet 48b and flows to the first inlet port 50a of the flow rate adjustment mechanism 50.

[0137] The heat medium radiator 49 of this embodiment is a heat exchanger having a plurality of tubes and a plurality of corrugated fins, similar to the air heat exchanger 48, for example. The heat medium radiator 49 radiates heat from the heat medium in the heat medium radiator 49 to the outside (for example, outside the vehicle 70).

[0138] Specifically, the heat medium radiator 49 is a heat exchanger that exchanges heat between the heat medium and the outside air, and has a heat medium inlet 49a into which the heat medium flows and a heat medium outlet 49b from which the heat medium flows out. The heat medium radiator 49 exchanges heat between the heat medium flowing into the heat medium inlet 49a from the pump 47 and the outside air passing through the heat medium radiator 49, and by this heat exchange, discharges the heat of the heat medium to the outside of the vehicle 70. The heat medium radiator 49 causes the heat medium after the heat exchange to flow from the heat medium outlet 49b to the second inlet port 50b of the flow rate adjustment mechanism 50.

[0139] The heat medium radiator 49 is disposed, for example, in the front of the vehicle 70 so that outside air as traveling wind hits it when the vehicle is traveling. With this arrangement, outside air as traveling wind is supplied to the heat medium radiator 49. Also, the vehicle 70 is configured such that outside air can be supplied to the heat medium radiator 49 even when the vehicle 70 is stopped by a blower (not shown).

[0140] The flow rate adjustment mechanism 50 of the present embodiment is an electric three-way valve controlled by a circuit control unit 80 (see FIG. 3). The flow rate adjustment mechanism 50 has a first inlet port 50a and a second inlet port 50b into which the heat medium flows, and an outlet port 50c from which the heat medium flows out. For example, the flow rate adjustment mechanism 50 has a valve body that increases and decreases the opening degrees of the first inlet port 50a and the second inlet port 50b, and an electric actuator that drives the valve body in accordance with control from the circuit control unit 80.

[0141] The flow rate adjustment mechanism 50 adjusts the flow rate ratio between the flow rate of the heat medium flowing through the air heat exchanger 48 and the flow rate of the heat medium flowing through the heat medium radiator 49. Specifically, the flow rate adjustment mechanism 50 has a structure in which the first inlet port 50a and the second inlet port 50b can be connected to and disconnected from the outlet port 50c, respectively, and increases and decreases the opening degrees of the first inlet port 50a and the second inlet port 50b with respect to the outlet port 50c. In the flow rate adjustment mechanism 50, as the opening degree of the first inlet port 50a increases, the opening degree of the second inlet port 50b decreases.

[0142] Also, the flow rate adjustment mechanism 50 is configured such that either the first inlet port 50a or the second inlet port 50b can be fully closed. For example, when the first inlet port 50a is fully closed, the opening degree of the second inlet port 50b becomes maximum in a state where the second inlet port 50b and the outlet port 50c are in communication. Conversely, when the second inlet port 50b is fully closed, the opening degree of the first inlet port 50a becomes maximum in a state where the first inlet port 50a and the outlet port 50c are in communication. Note that fully closing the first and second inlet ports 50a and 50b means that the inlet port is blocked and the flow of the heat medium at the inlet port is blocked, that is, the opening degree of the inlet port is zero.

[0143] With such a configuration, when the pump 47 of the heat medium circuit 46 is operating, the greater the opening degree of the first inlet port 50a, the greater the flow rate of the heat medium flowing through the air heat exchanger 48 connected to the first inlet port 50a. Also, the greater the opening degree of the second inlet port 50b, the greater the flow rate of the heat medium flowing through the heat medium radiator 49 connected to the second inlet port 50b. And the heat medium circulating in the heat medium circuit 46 may flow through either the air heat exchanger 48 or the heat medium radiator 49, or may flow through both the air heat exchanger 48 and the heat medium radiator 49, depending on the state of the flow rate adjustment mechanism 50.

[0144] Except for what has been described above, the heat medium circuit 46 of the present embodiment is the same as the heat medium circuit 30 of the first embodiment.

[0145] The temperature control device 10 of the present embodiment is configured as described above. For example, when the temperature-controlled air Ac is heated by this temperature control device 10, the compressor 13 of the refrigeration cycle 12 and the pump 47 of the heat medium circuit 46 are operated. And the flow rate adjustment mechanism 50 opens the first inlet port 50a and communicates the first inlet port 50a and the outlet port 50c.

[0146] Thereby, in the refrigeration cycle 12, the refrigerant circulates from the compressor 13 in the order of the refrigerant radiator 42, the expansion valve 16, and the evaporator 17 and returns to the compressor 13. And the refrigerant circulating in the refrigeration cycle 12 evaporates in the evaporator 17 and absorbs heat from the forward blowing air Af (see FIG. 1), condenses in the refrigerant radiator 42, and releases heat to the heat medium of the heat medium circuit 46. As a result, the heat medium of the heat medium circuit 46 is heated by the refrigerant radiator 42. In this case, the forward blowing air Af is cooled by the evaporator 17. For example, the cooled forward blowing air Af is heated as necessary by a heater core disposed in an air conditioning unit (not shown) having the evaporator 17 and then blown into the front passenger compartment 71a.

[0147] In the heat medium circuit 46, the heat medium heated by the refrigerant radiator 42 flows from the refrigerant radiator 42 through the pump 47 to the air heat exchanger 48, and releases heat to the air Ac to be temperature-controlled in the air heat exchanger 48. As a result, the air Ac to be temperature-controlled passing through the air heat exchanger 48 is heated. The heat medium that has released heat in the air heat exchanger 48 flows from the air heat exchanger 48 through the flow rate adjustment mechanism 50 to the refrigerant radiator 42, and is reheated by the refrigerant radiator 42.

[0148] At this time, the flow rate adjustment mechanism 50 may communicate not only the first inlet port 50a but also the second inlet port 50b with the outlet port 50c. However, in this embodiment, the second inlet port 50b is fully closed.

[0149] When the front blowing air Af is cooled by the temperature control device 10 without the air Ac to be temperature-controlled being heated, the compressor 13 of the refrigeration cycle 12 and the pump 47 of the heat medium circuit 46 are operated. Then, the flow rate adjustment mechanism 50 communicates the second inlet port 50b with the outlet port 50c while fully closing the first inlet port 50a.

[0150] Thereby, the refrigerant circulating in the refrigeration cycle 12 condenses in the refrigerant radiator 42 and releases heat to the heat medium of the heat medium circuit 46, evaporates in the evaporator 17, and absorbs heat from the front blowing air Af. In this way, the front blowing air Af is cooled.

[0151] In the heat medium circuit 46, the heat medium heated by the refrigerant radiator 42 flows from the refrigerant radiator 42 through the pump 47 to the heat medium radiator 49, and releases heat to the outside air in the heat medium radiator 49. The heat medium that has released heat in the heat medium radiator 49 flows from the heat medium radiator 49 through the flow rate adjustment mechanism 50 to the refrigerant radiator 42, and is reheated by the refrigerant radiator 42. At this time, since the first inlet port 50a is fully closed as described above, the heat medium does not flow through the air heat exchanger 48, and heat exchange in the air heat exchanger 48 does not occur.

[0152] As described above, according to the present embodiment, the refrigeration cycle 12 includes a compressor 13, a refrigerant radiator 42, an expansion valve 16, and an evaporator 17. In the heat medium circuit 46, the heat medium circulates while flowing through at least one of the air heat exchanger 48 and the heat medium radiator 49 and the refrigerant radiator 42. The flow rate adjustment mechanism 50 of the heat medium circuit 46 adjusts the flow rate ratio between the flow rate of the heat medium flowing through the air heat exchanger 48 and the flow rate of the heat medium flowing through the heat medium radiator 49. The evaporator 17 evaporates the refrigerant and cools the forward blowing air Af by heat-exchanging the refrigerant with the forward blowing air Af. The refrigerant radiator 42 heats the heat medium by heat-exchanging the refrigerant with the heat medium of the heat medium circuit 46. Then, the heat medium radiator 49 of the heat medium circuit 46 dissipates heat from the heat medium to the outside (for example, outside the vehicle 70), and the air heat exchanger 48 heats the temperature control target air Ac by heat-exchanging the heat medium with the temperature control target air Ac.

[0153] Therefore, it is possible to warm the temperature control target air Ac using the refrigeration cycle 12 for cooling the forward blowing air Af. In other words, it is possible to make the refrigeration cycle 12 for cooling the forward blowing air Af also have the function of warming the temperature control target air Ac.

[0154] And in the temperature control device 10 of the present embodiment, heat is transferred by the heat medium between each of the air heat exchanger 48 and the heat medium radiator 49 and the refrigerant radiator 42. Therefore, it is possible to avoid the situation that the arrangement of the refrigerant radiator 42 is restricted because the function of warming the temperature control target air Ac is added to the refrigeration cycle 12. Therefore, regardless of the arrangement of the air heat exchanger 48 and the heat medium radiator 49, for example, the refrigeration cycle 12 can be configured compactly, so that the temperature control device 10 can have a simple configuration.

[0155] (1) Also, according to the present embodiment, the heat medium circuit 46 has a pump 47 that circulates the heat medium in the heat medium circuit 46 and can increase or decrease the flow rate of the heat medium. Therefore, it is possible to freely adjust the flow rate of the heat medium flowing through the refrigerant radiator 42 according to the amount of heat radiated from the refrigerant to the heat medium in the refrigerant radiator 42.

[0156] Except for what has been described above, this embodiment is the same as the first embodiment. And in this embodiment, the effects resulting from the configurations common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment.

[0157] (Seventh Embodiment) Next, the seventh embodiment will be described. In this embodiment, the differences from the aforementioned sixth embodiment will mainly be described.

[0158] As shown in FIG. 11, the heat medium circuit 46 of this embodiment has a heat exchange plate 51 as a heat exchange part instead of the air heat exchanger 48 (see FIG. 9) of the sixth embodiment.

[0159] The heat exchange plate 51 of this embodiment heats the object 74 to be temperature-controlled (see FIG. 5) by the heat medium flowing inside the heat exchange plate 51. Except for this, the heat exchange plate 51 of this embodiment is the same as the heat exchange plate 33 of the second embodiment.

[0160] Therefore, the heat exchange plate 51 of this embodiment is provided, for example, in the space 75a inside the cup holder as shown in FIG. 5, and warms a beverage cup or the like, which is the object 74 to be temperature-controlled placed on the heat exchange plate 51. Also in this embodiment, the object 74 to be temperature-controlled corresponds to the object to be temperature-controlled of the present disclosure in the same manner as in the second embodiment.

[0161] Further, the heat exchange plate 51 has a heat medium inlet 51a for allowing the heat medium to flow into the internal flow path of the heat exchange plate 51 and a heat medium outlet 51b for allowing the heat medium to flow out from the internal flow path. The heat medium inlet 51a of the heat exchange plate 51 is connected to the discharge port 47a of the pump 47, and the heat medium outlet 51b of the heat exchange plate 51 is connected to the first inlet port 50a of the flow rate adjustment mechanism 50.

[0162] As described above, according to the present embodiment, as shown in FIGS. 5 and 11, the heat medium circuit 46 has a heat exchange plate 51. The heat exchange plate 51 exchanges heat between the temperature control object 74 in contact with the heat exchange plate 51 and the heat medium flowing through the heat exchange plate 51 by heat conduction, thereby heating the temperature control object 74. Therefore, it is possible to heat the temperature control object 74 by heat conduction without the need for blowing air.

[0163] Except for what has been described above, this embodiment is the same as the sixth embodiment. And in this embodiment, the effects achieved by the configuration common to the aforementioned sixth embodiment can be obtained in the same manner as in the sixth embodiment.

[0164] (Eighth Embodiment) Next, the eighth embodiment will be described. In this embodiment, the differences from the aforementioned first embodiment will be mainly described.

[0165] As shown in FIG. 12, the temperature control device 10 of this embodiment has a function of cooling the forward blowing air Af, but does not have a function of cooling the rearward blowing air Ab. Instead, the temperature control device 10 of this embodiment has a function of heating the temperature control air Ac sent to the temperature control space 77 of FIG. 10 and a function of cooling the temperature control air Ac. In short, the temperature control device 10 of this embodiment has a configuration that combines the temperature control device 10 of the first embodiment and the temperature control device 10 of the sixth embodiment.

[0166] The temperature control device 10 of this embodiment, similar to the first embodiment, includes a refrigeration cycle 12, a heat medium circuit 30, and a circuit control unit 80. Furthermore, the temperature control device 10 of this embodiment also includes the heat medium circuit 46 of the sixth embodiment. The circuit control unit 80 of this embodiment is the same as the circuit control unit 80 of the first embodiment except that the objects to be controlled are the refrigeration cycle 12 and the two heat medium circuits 30 and 46.

[0167] In this embodiment, since two heat medium circuits 30 and 46 are provided, the heat medium circuit 46 similar to that of the sixth embodiment is referred to as the first heat medium circuit 46, and the heat medium circuit 30 similar to that of the first embodiment is referred to as the second heat medium circuit 30. Also, the air heat exchanger 48 of the first heat medium circuit 46 is referred to as the first air heat exchanger 48 and is provided as the first heat exchange unit, the pump 47 of the first heat medium circuit 46 is referred to as the first pump 47, and the heat medium of the first heat medium circuit 46 is referred to as the first heat medium. Further, the air heat exchanger 32 of the second heat medium circuit 30 is referred to as the second air heat exchanger 32 and is provided as the second heat exchange unit, the pump 31 of the second heat medium circuit 30 is referred to as the second pump 31, and the heat medium of the second heat medium circuit 30 is referred to as the second heat medium.

[0168] The refrigeration cycle 12 of this embodiment has the refrigerant radiator 42 of the sixth embodiment instead of the refrigerant radiator 14 of the first embodiment. And in the refrigeration cycle 12 of this embodiment, the refrigerant inlet 42a of the refrigerant radiator 42 is connected to the discharge port 13a of the compressor 13, and the refrigerant outlet 42b of the refrigerant radiator 42 is connected to the refrigerant inlet 16a of the first expansion valve 16 and the refrigerant inlet 20a of the second expansion valve 20.

[0169] The first air heat exchanger 48 of this embodiment exchanges heat between the first heat medium and the temperature-controlled air Ac (see FIG. 10) as the first temperature-controlled object, and heats the temperature-controlled air Ac by this heat exchange.

[0170] Also, the second air heat exchanger 32 of this embodiment exchanges heat between the second heat medium and the temperature-controlled air Ac (see FIG. 10) as the second temperature-controlled object, and cools the temperature-controlled air Ac by this heat exchange. Therefore, in this embodiment, since both the above-mentioned first temperature-controlled object and the second temperature-controlled object are the temperature-controlled air Ac, they are the same temperature-controlled object.

[0171] Except for what has been described above, the refrigerant radiator 42 of this embodiment is the same as the refrigerant radiator 42 of the sixth embodiment, and the refrigeration cycle 12 of this embodiment is the same as the refrigeration cycle 12 of the first embodiment. Also, except for what has been described above, the first heat medium circuit 46 of this embodiment is the same as the heat medium circuit 46 of the sixth embodiment, and the second heat medium circuit 30 of this embodiment is the same as the heat medium circuit 30 of the first embodiment.

[0172] The temperature control device 10 of this embodiment is as described above. For example, when the temperature-controlled target air Ac is heated by this temperature control device 10, the compressor 13 of the refrigeration cycle 12 and the first pump 47 of the first heat medium circuit 46 are operated, and the second pump 31 of the second heat medium circuit 30 is stopped. Also, the flow rate adjustment mechanism 50 opens the first inlet port 50a and communicates the first inlet port 50a and the outlet port 50c.

[0173] Also, the first expansion valve 16 is set to a state where the refrigerant can flow, and while the throttle opening degree of the first expansion valve 16 is adjusted so that the first expansion valve 16 exhibits a pressure-reducing action, the second expansion valve 20 is fully closed. By fully closing this second expansion valve 20, a situation where the temperature-controlled target air Ac, which is the object to be heated, is cooled by the air second heat exchanger 32 is avoided.

[0174] Due to the above-described various operations and the like, in the refrigeration cycle 12, the refrigerant circulates from the compressor 13 through the refrigerant radiator 42, the first expansion valve 16, and the first evaporator 17 in this order and returns to the compressor 13, but does not flow through the second evaporator 21. And in the first heat medium circuit 46, the first heat medium heated by the refrigerant radiator 42 flows from the refrigerant radiator 42 through the first pump 47 to the first heat exchanger 48 for air, and releases heat to the temperature-controlled target air Ac in the first heat exchanger 48 for air. Thereby, the temperature-controlled target air Ac passing through the first heat exchanger 48 for air is heated.

[0175] Therefore, in this case, the operation of the refrigeration cycle 12 of the present embodiment is the same as the operation of the refrigeration cycle 12 when the air Ac to be temperature-controlled is heated in the sixth embodiment. And the operation of the first heat medium circuit 46 of the present embodiment is the same as the operation of the heat medium circuit 46 when the air Ac to be temperature-controlled is heated in the sixth embodiment.

[0176] At this time, the flow rate adjustment mechanism 50 may communicate not only the first inlet port 50a but also the second inlet port 50b with the outlet port 50c. However, also in the present embodiment, as in the sixth embodiment, the second inlet port 50b is fully closed.

[0177] Also, when the air Ac to be temperature-controlled is cooled by the temperature control device 10, the compressor 13 of the refrigeration cycle 12, the first pump 47 of the first heat medium circuit 46, and the second pump 31 of the second heat medium circuit 30 are operated. Also, the second expansion valve 20 is set in a state where the refrigerant can flow, and the throttle opening degree of the second expansion valve 20 is adjusted so that the second expansion valve 20 exhibits a pressure-reducing action.

[0178] Also, the flow rate adjustment mechanism 50 fully closes the first inlet port 50a while communicating the second inlet port 50b and the outlet port 50c. By fully closing the first inlet port 50a of the flow rate adjustment mechanism 50, a situation where the air Ac to be temperature-controlled, which is the object to be cooled, is heated by the first heat exchanger 48 for air is avoided.

[0179] Due to each of the above operations and the like, in the refrigeration cycle 12, the refrigerant circulating in the refrigeration cycle 12 evaporates in the second evaporator 21 and absorbs heat from the second heat medium in the second heat medium circuit 30, and condenses in the refrigerant radiator 42 and releases heat to the first heat medium in the first heat medium circuit 46. In the first heat medium circuit 46, the first heat medium heated by the refrigerant radiator 42 flows from the refrigerant radiator 42 through the first pump 47 to the heat medium radiator 49, and releases heat to the outside air in the heat medium radiator 49. The heat medium that has released heat in the heat medium radiator 49 flows from the heat medium radiator 49 through the flow rate adjustment mechanism 50 to the refrigerant radiator 42 and is reheated by the refrigerant radiator 42. At this time, since the first inlet port 50a is fully closed as described above, the first heat medium does not flow through the first air heat exchanger 48, and heat exchange in the first air heat exchanger 48 does not occur.

[0180] And in the second heat medium circuit 30, the second heat medium circulating in the second heat medium circuit 30 absorbs heat from the air Ac to be temperature-controlled in the second air heat exchanger 32 and releases heat to the refrigerant in the refrigeration cycle 12 in the second evaporator 21. In this way, the air Ac to be temperature-controlled is cooled.

[0181] At this time, the forward blowing air Af may or may not be cooled by the temperature control device 10. For example, when the forward blowing air Af is not cooled by the temperature control device 10, the first expansion valve 16 is fully closed.

[0182] On the other hand, when the forward blowing air Af is also cooled by the temperature control device 10 together with the air Ac to be temperature-controlled, the first expansion valve 16 is also set in a state where the refrigerant can flow, and the throttle opening of the first expansion valve 16 is adjusted so that the first expansion valve 16 exhibits a pressure-reducing action. Thereby, the refrigerant in the refrigeration cycle 12 evaporates in the first evaporator 17 and absorbs heat from the forward blowing air Af. Then, the refrigerant flowing out of the first evaporator 17 and the refrigerant flowing out of the second evaporator 21 are both sucked into the suction port 13b of the compressor 13. In this way, the forward blowing air Af is also cooled.

[0183] Also, when the front blowing air Af is cooled without heating or cooling the temperature control target air Ac by the temperature control device 10, the compressor 13 of the refrigeration cycle 12 and the first pump 47 of the first heat medium circuit 46 are operated, and the second pump 31 of the second heat medium circuit 30 is stopped. Further, the flow rate adjustment mechanism 50 communicates the second inlet port 50b and the outlet port 50c while closing the first inlet port 50a completely. Also, the first expansion valve 16 is set to a state where the refrigerant can flow, and the throttle opening of the first expansion valve 16 is adjusted so that the first expansion valve 16 exhibits a pressure reducing action, while the second expansion valve 20 is closed completely.

[0184] Thereby, the refrigerant circulating in the refrigeration cycle 12 condenses in the refrigerant radiator 42 and dissipates heat to the first heat medium of the first heat medium circuit 46, and evaporates in the first evaporator 17 and absorbs heat from the front blowing air Af. In this way, the front blowing air Af is cooled.

[0185] And in the first heat medium circuit 46, the first heat medium heated by the refrigerant radiator 42 flows from the refrigerant radiator 42 through the first pump 47 to the heat medium radiator 49, and dissipates heat to the outside air in the heat medium radiator 49. The first heat medium that has dissipated heat in the heat medium radiator 49 flows from the heat medium radiator 49 through the flow rate adjustment mechanism 50 to the refrigerant radiator 42 and is heated again in the refrigerant radiator 42. At this time, since the first inlet port 50a is completely closed as described above, the first heat medium does not flow through the first air heat exchanger 48, and heat exchange in the first air heat exchanger 48 does not occur.

[0186] (1) As described above, according to this embodiment, the refrigerant radiator 42 of the refrigeration cycle 12 heats the first heat medium by heat-exchanging the refrigerant with the first heat medium of the first heat medium circuit 46. Then, the first air heat exchanger 48 of the first heat medium circuit 46 heats the temperature-controlled air Ac (see FIG. 10) by heat-exchanging the first heat medium with the temperature-controlled air Ac. On the other hand, the second evaporator 21 of the refrigeration cycle 12 evaporates the refrigerant and cools the second heat medium by heat-exchanging the refrigerant with the second heat medium of the second heat medium circuit 30. Then, the air heat exchanger 32 of the second heat medium circuit 30 cools the temperature-controlled air Ac by heat-exchanging the second heat medium with the temperature-controlled air Ac. Therefore, it is possible to heat or cool the temperature-controlled air Ac sent to the temperature-controlled space 77 of FIG. 10 using the temperature control device 10 of this embodiment.

[0187] Also, according to this embodiment, when the flow rate adjustment mechanism 50 allows the first heat medium to flow to the first air heat exchanger 48, in the refrigeration cycle 12, the refrigerant flows from the refrigerant radiator 42 to the first evaporator 17, while the flow of the refrigerant from the refrigerant radiator 42 to the second evaporator 21 is blocked. Thereby, when the temperature-controlled air Ac is heated, it is possible to avoid the situation where the temperature-controlled air Ac, which is the object to be heated, is cooled by the second air heat exchanger 32.

[0188] Also, according to this embodiment, when the refrigerant of the refrigeration cycle 12 flows from the refrigerant radiator 42 to the second evaporator 21, the flow rate adjustment mechanism 50 allows the first heat medium to flow to the heat medium radiator 49 while blocking the flow of the first heat medium to the first air heat exchanger 48. Thereby, when the temperature-controlled air Ac is cooled, it is possible to avoid the situation where the temperature-controlled air Ac, which is the object to be cooled, is heated by the first air heat exchanger 48.

[0189] Except for what has been described above, this embodiment is the same as the first embodiment. And in this embodiment, the effects resulting from the configurations common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment. Also, in this embodiment, since the configuration common to the aforementioned sixth embodiment is also provided, the effects resulting from the configuration common to the sixth embodiment can be obtained in the same manner as in the sixth embodiment.

[0190] Note that although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with any one of the aforementioned second to fifth embodiments and the seventh embodiment.

[0191] (Ninth Embodiment) Next, the ninth embodiment will be described. In this embodiment, the differences from the aforementioned eighth embodiment will be mainly described.

[0192] As shown in FIG. 13, in this embodiment, the circuit configurations of the refrigeration cycle 12, the first heat medium circuit 46, and the second heat medium circuit 30 are the same as those in the eighth embodiment, respectively.

[0193] Specifically, in this embodiment, the first air heat exchanger 48 and the second air heat exchanger 32 are integrally configured by means such as bolting, and constitute a composite heat exchanger 52. In the composite heat exchanger 52, for example, the first air heat exchanger 48 and the second air heat exchanger 32 are laminated, and one of the first air heat exchanger 48 and the second air heat exchanger 32 is arranged upstream of the other in the flow direction of the air Ac to be temperature-controlled.

[0194] (1) As described above, according to this embodiment, the first air heat exchanger 48 and the second air heat exchanger 32 are integrally configured. Therefore, the location for cooling the air Ac to be temperature-controlled and the location for heating the air Ac to be temperature-controlled are aggregated in the composite heat exchanger 52, so that it is possible to make the temperature control device 10 a compact and simple system.

[0195] Except for what has been described above, this embodiment is the same as the eighth embodiment. And in this embodiment, the effects resulting from the configurations common to the aforementioned eighth embodiment can be obtained in the same manner as in the eighth embodiment.

[0196] (Tenth Embodiment) Next, the tenth embodiment will be described. In this embodiment, the differences from the aforementioned first embodiment will mainly be described.

[0197] As shown in FIGS. 1 and 14, the air heat exchanger 32 of this embodiment cools the luggage compartment air as the object to be temperature-controlled, which is the air sent to the luggage compartment 78, rather than the rearward blowing air Ab. The luggage compartment 78 is formed as a temperature-controlled space provided inside the vehicle 70 and separated from the outside of the vehicle 70. For example, the luggage compartment 78 is provided above the engine room that houses a radiator 79 for dissipating heat from the engine cooling water and an engine, etc., and is formed so as to be separated from the engine room. Therefore, the luggage compartment 78 is located around the passenger compartment space 71.

[0198] Except for what has been described above, this embodiment is the same as the first embodiment. And in this embodiment, the effects resulting from the configurations common to the aforementioned first embodiment can be obtained in the same manner as in the first embodiment.

[0199] Note that although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with any one of the aforementioned third to sixth embodiments, eighth embodiment, and ninth embodiment.

[0200] (Other Embodiments) (1) In each of the above-described embodiments, as shown in FIG. 1, the vehicle 70 equipped with the temperature control device 10 is, for example, a hybrid vehicle, but it may also be an electric vehicle or an engine vehicle without a driving motor. Furthermore, the temperature control device 10 may not be mounted on the vehicle 70.

[0201] (2) In each of the above-described embodiments, for example, the refrigeration cycle 12 shown in FIG. 1 is operated as a subcritical refrigeration cycle in which the refrigerant pressure on the high-pressure side within the cycle does not exceed the critical pressure of the refrigerant, but this is just an example. For example, the refrigeration cycle 12 may be operated as a supercritical cycle in which the refrigerant pressure on the high-pressure side within the cycle becomes equal to or higher than the critical pressure of the refrigerant.

[0202] (3) In the above-described second embodiment, as shown in FIG. 5, the temperature adjustment chamber in which the heat exchange plate 33 is provided is the space 75a within the cup holder, but this is just an example. For example, the temperature adjustment chamber may be the internal space of a storage compartment in which small items, food and drink, etc. are stored.

[0203] (4) In the above-described first embodiment, as shown in FIGS. 1 and 2, the air heat exchanger 32 is a heat exchanger that cools the rearward blowing air Ab as the temperature adjustment target, but this is just an example. For example, as shown in FIG. 15, the air heat exchanger 32 may cool the temperature adjustment target air Ac as the temperature adjustment target sent to the temperature adjustment space 77 described in the sixth embodiment, for example.

[0204] (5) In the above-described sixth embodiment, as shown in FIGS. 9 and 10, the air heat exchanger 48 is a heat exchanger that warms the temperature adjustment target air Ac as the temperature adjustment target, but this is just an example. For example, the air heat exchanger 48 may warm the rearward blowing air Ab (see FIG. 2) as the temperature adjustment target.

[0205] (6) In the above-described eighth embodiment, both the first temperature adjustment target heated by the first air heat exchanger 48 and the second temperature adjustment target cooled by the second air heat exchanger 32 are the temperature adjustment target air Ac and are the same, but this is just an example. For example, the first temperature adjustment target may be the temperature adjustment target air Ac in FIG. 10, and the second temperature adjustment target may be the rearward blowing air Ab in FIG. 2, and it may be acceptable. Also, the first temperature adjustment target and the second temperature adjustment target may not be the temperature adjustment target air Ac.

[0206] (7) In the above-described first embodiment, the first expansion valve 16 and the second expansion valve 20 shown in FIG. 1 are each configured to be fully closable, but this is just an example. For example, the first expansion valve 16 may not be fully closable, and an on-off valve may be provided at the refrigerant inlet 16a of the first expansion valve 16. Similarly, the second expansion valve 20 may not be fully closable, and an on-off valve may be provided at the refrigerant inlet 20a of the second expansion valve 20.

[0207] (8) It should be noted that the present invention is not limited to the above-described embodiments and can be implemented with various modifications. Also, the above embodiments are not independent of each other, and can be appropriately combined except when the combination is clearly impossible.

[0208] Moreover, in each of the above embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential except when it is explicitly stated that they are essential and when they are considered to be clearly essential in principle. Also, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, and range of the components of the embodiment are mentioned, they are not limited to that specific number except when it is explicitly stated that they are essential and when they are clearly limited to a specific number in principle. Further, in each of the above embodiments, when referring to the material, shape, positional relationship, etc. of the components, etc., they are not limited to that material, shape, positional relationship, etc. except when it is explicitly stated and when they are clearly limited to a specific material, shape, positional relationship, etc. in principle.

[0209] In addition, the circuit control unit 80 and its method described in the present disclosure may be implemented by a dedicated computer configured by a processor and a memory programmed to execute one or more functions embodied by a computer program. Alternatively, the circuit control unit 80 and its method described in the present disclosure may be implemented by a dedicated computer configured by a processor constituted by one or more dedicated hardware logic circuits. Or, the circuit control unit 80 and its method described in the present disclosure may be implemented by one or more dedicated computers configured by a combination of a processor and a memory programmed to execute one or more functions and a processor constituted by one or more hardware logic circuits. Further, the computer program may be stored in a computer-readable non-transitory tangible recording medium as instructions executable by a computer.

Description of Reference Numerals

[0210] 10 Temperature control device 12 Refrigeration cycle 13 Compressor 14, 42 Refrigerant radiator 16 First expansion valve 17 First evaporator 20 Second expansion valve 21 Second evaporator 30 Heat medium circuit 32 Air heat exchanger

Claims

1. A temperature control device for adjusting the temperature of a temperature control target (74, Ab, Ac), comprising: A refrigerator cycle (12) having a compressor (13) for compressing a refrigerant, a refrigerant radiator (42) for dissipating heat from the refrigerant flowing out of the compressor, a first expansion valve (16) for decompressing the refrigerant flowing out of the refrigerant radiator, a first evaporator (17) for evaporating the refrigerant flowing out of the first expansion valve and then flowing the refrigerant to the compressor, a second expansion valve (20) for decompressing the refrigerant flowing out of the refrigerant radiator, and a second evaporator (21) for evaporating the refrigerant flowing out of the second expansion valve and then flowing the refrigerant to the compressor; A first heat medium circuit (46) having a first heat exchange section (48, 51), a heat medium radiator (49), and a flow rate adjustment mechanism (50), wherein a first heat medium circulates while flowing through at least one of the first heat exchange section and the heat medium radiator and the refrigerant radiator; A second heat medium circuit (30) having a second heat exchange section (32, 33), wherein a second heat medium circulates while flowing through the second heat exchange section and the second evaporator; The first evaporator evaporates the refrigerant by exchanging heat between the blown air (Af) sent to the air-conditioned target space (71a) and the refrigerant, and cools the blown air. The second evaporator evaporates the refrigerant by exchanging heat between the second heat medium and the refrigerant, and cools the second heat medium. The second heat exchange section cools the temperature control target by exchanging heat between the temperature control target and the second heat medium. The flow rate adjustment mechanism adjusts the flow rate ratio between the flow rate of the first heat medium flowing through the first heat exchange section and the flow rate of the first heat medium flowing through the heat medium radiator. The refrigerant radiator heats the first heat medium by exchanging heat between the first heat medium and the refrigerant. The heat medium radiator dissipates heat from the first heat medium. The first heat exchange section heats the temperature control target by exchanging heat between the temperature control target and the first heat medium. The refrigeration cycle is configured to be able to block the flow of the refrigerant from the refrigerant radiator to the second evaporator. When the flow rate adjusting mechanism circulates the first heat medium to the first heat exchange part, in the refrigeration cycle, the refrigerant flows from the refrigerant radiator to the first evaporator, while the flow of the refrigerant from the refrigerant radiator to the second evaporator is blocked. When the refrigerant in the refrigeration cycle flows from the refrigerant radiator to the second evaporator, the flow rate adjusting mechanism circulates the first heat medium to the heat medium radiator while blocking the flow of the first heat medium to the first heat exchange part, a temperature control device.

2. The temperature control device according to claim 1, wherein the first heat exchange part and the second heat exchange part are integrally formed.

3. The refrigeration cycle has a pressure regulating valve (23). The pressure regulating valve is provided on the downstream side of the refrigerant flow of the first evaporator and on the upstream side of the refrigerant flow of the compressor, and maintains the refrigerant pressure of the first evaporator at a predetermined value or more. The temperature control device according to claim 1 or 2.

4. The second heat medium circuit has a battery heat exchanger (34). In the second heat medium circuit, the second heat medium also flows through the battery heat exchanger. The battery heat exchanger exchanges heat between the battery (76) and the second heat medium. The temperature control device according to claim 1 or 2.

5. It includes a fluid circuit (36) having a battery heat exchanger (34). The refrigeration cycle has a third expansion valve (24) for decompressing the refrigerant flowing out from the refrigerant radiator, and a third evaporator (25) for evaporating the refrigerant flowing out from the third expansion valve and then flowing it to the compressor. In the fluid circuit, the fluid for battery cooling circulates while flowing through the battery heat exchanger and the third evaporator. The third evaporator evaporates the refrigerant by exchanging heat between the fluid for battery cooling and the refrigerant, and cools the fluid for battery cooling. The battery heat exchanger heat-exchanges the battery (76) and the battery cooling fluid, and the temperature control device according to claim 1 or 2.

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