Temperature control system and temperature control method for vehicle

Abstract

The present invention relates to an improvement in a system which is provided with a first circuit and a second circuit that can be divided as a circuit for a heat medium, and which is provided with a mechanism capable of coping with a volume change caused by a temperature change of the heat medium. The heat medium circuit is provided with: a high-pressure-side heat exchanger; a low-pressure-side heat exchanger; an outdoor heat exchanger; a temperature control device; a reservoir tank configured so as to be able to connect the suction parts of the first pump and the second pump; and a connection valve that provides either one connection state in which one of the first pump and the second pump is connected or both connection states in which both of the first pump and the second pump are connected as a connection state with the liquid storage tank. The heat medium circuit is configured so that a first circuit including the low-pressure-side heat exchanger and corresponding to the first pump and a second circuit including the high-pressure-side heat exchanger and corresponding to the second pump can be set in parallel. In addition, a series circuit corresponding to the first pump and the second pump, including the low-pressure-side heat exchanger and the high-pressure-side heat exchanger arranged in series, can be set.

Description

Technical Field

[0001] The invention relates to a temperature control system assembled on a vehicle and a temperature control method using the temperature control system. Background Art

[0002] In electric vehicles and hybrid vehicles that obtain driving force for the vehicle from engines and motors, when the heat source is easily insufficient, in addition to the air conditioning functions required by the vehicle, such as heating and cooling, dehumidification, and ventilation, thermal management and waste heat utilization of vehicle-mounted equipment such as batteries are required. In the past, in addition to heat pump systems, multiple systems have been used to meet such requirements, such as systems including a cooler for cooling the battery and a heater for heating the battery, or systems that use a pump to transport water heated by waste heat from a radiator to a temperature control target.

[0003] As a thermal management system for a vehicle, there has been proposed a system including a primary circuit in which a refrigerant circulates according to a refrigeration cycle and a secondary circuit in which a heat medium (water, etc.) is pumped to an indoor air conditioning unit (for example, Patent Documents 1 and 2).

[0004] The system described in Patent Document 1 discloses using cooling water to cool an electric device and a storage battery. The system comprises: a liquid storage tank storing cooling water cooled by a radiator; a cooling water pipeline including a radiator and a liquid storage tank for circulating cooling water supplied from the liquid storage tank to the electric device; and other cooling water pipelines for circulating cooling water supplied from the liquid storage tank to the storage battery through the same liquid storage tank. A pump and a valve are provided on each cooling water pipeline, and one or both of the electric device and the storage battery are cooled according to the opening and closing state of the valve. In addition, the storage tank has the function of receiving excess heating medium when the volume of the heating medium increases due to a rise in temperature, and replenishing the heating medium in the pipe when the temperature drops.

[0005] Furthermore, the system described in Patent Document 2 discloses a structure capable of supplying a heat medium to a plurality of devices. The system includes a cold water circuit including a cooler core and a first pump, a warm water circuit including a heater core and a second pump, and a first switching valve and a second switching valve. A closed liquid storage tank is connected to the warm water circuit, and the closed liquid storage tank is used to store the heat medium and maintain the pressure of the heat medium within an appropriate range. Previous technical literature Patent Literature

[0006] Patent Document 1: Japanese Patent Application Publication No. 2021-37931 Patent Document 2: Japanese Patent No. 6064753 Summary of the invention Technical issues to be solved by the invention

[0007] In the system described in Patent Document 1, the cooling water pipeline including the radiator and other cooling water pipelines pass through the same reservoir. Therefore, if both pipelines are connected and the system is operated in a state where the path of the cooling water including both pipelines is set, the cooling water flowing in the path will not flow in the original path ahead of the reservoir, but will flow in a short path through the reservoir. That is, the cooling water flows in a path with a smaller pressure loss than the original path through the reservoir.

[0008] Furthermore, the system described in Patent Document 2 has a closed liquid storage tank in the warm water circuit, but no liquid storage tank in the cold water circuit. Therefore, when the system is operated in a state where the warm water circuit and the cold water circuit are separated, as the temperature of the heat medium in the cold water circuit rises, the pressure in the piping of the cold water circuit increases. However, considering the increase in cost or the enlargement of the system, and the mixing of air caused by the deviation of the liquid storage amount in the two liquid storage tanks, it is difficult to install a liquid storage tank in the cold water circuit to avoid the above problems.

[0009] As described above, the present invention relates to a system having a first circuit and a second circuit that can be divided as circuits of a heat medium, and having a mechanism that can cope with volume changes caused by temperature changes of the heat medium. The present invention aims to provide a temperature control system and a temperature control method for a vehicle, which can ensure the required capacity by allowing the heat medium to flow in a predetermined path even when the first circuit and the second circuit are continuous, and can avoid excessive internal pressure of the piping even when the first circuit and the second circuit are divided. Means for solving technical problems

[0010] The present invention is a temperature control system for a vehicle, which comprises: a refrigerant circuit, including a compressor, a high-pressure side heat exchanger, a pressure reducing unit and a low-pressure side heat exchanger, configured so that the refrigerant can circulate according to a refrigeration cycle; and a heat carrier circuit, configured so that a heat carrier that performs heat exchange with the refrigerant can circulate. The heat carrier circuit includes: a high-pressure side heat exchanger for performing heat exchange between the refrigerant and the heat carrier; a low-pressure side heat exchanger for performing heat exchange between the refrigerant and the heat carrier; a first pump and a second pump configured to pressurize the heat carrier; an outdoor heat exchanger for performing heat exchange between the outside air and the heat carrier; a temperature control device, which corresponds to a temperature control object heated or cooled by the heat carrier, or is used to heat or cool the temperature control object; a liquid storage tank, which can store the heat carrier and is configured to be connected to the respective suction parts of the first pump and the second pump; and a connecting valve, which is configured to give the first pump and the second pump any one of a single connection state of one connection side and a double connection state of both connection sides as a connection state with the liquid storage tank. The heat carrier circuit is constructed so that a first circuit including a low-pressure side heat exchanger and corresponding to a first pump and a second circuit including a high-pressure side heat exchanger and corresponding to a second pump can be set in parallel; and is constructed so that a series circuit including a low-pressure side heat exchanger and a high-pressure side heat exchanger arranged in series and corresponding to the first pump and the second pump can be set.

[0011] Furthermore, the present invention can be extended to a temperature control method for a vehicle. Effects of the Invention

[0012] According to the circuit structure set in the heat carrier circuit, as the connection state of the suction part of the first and second pumps with the liquid storage tank, it is possible to select any state of a one-way connection state in which only one of the first and second pumps is connected and a two-way connection state in which both are connected through the connection valve. In this way, even if the first and second circuits as the circuits of the heat carrier are divided, it is possible to avoid the internal pressure of the piping of the heat carrier from becoming too high or the piping from becoming negative pressure for any of the first and second circuits. Furthermore, even in the state of using a series circuit equivalent to the state in which the first and second circuits are connected, it is possible to avoid the heat carrier from bypassing the heat exchanger through the path that connects the suction parts of the first and second pumps with the liquid storage tank, thereby ensuring the necessary capacity. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 1 is a circuit diagram showing the vehicle temperature control system according to the first embodiment (cooling mode). Figure 2 It is shown Figure 1 A diagram of the system operating in heat pump mode. Figure 3 It is shown Figure 1 A diagram of the system operating in heater mode. Figure 4 This is a circuit diagram (heater mode) showing a vehicle temperature control system according to a first modification of the first embodiment. Figure 5 This is a circuit diagram (heater mode) showing a vehicle temperature control system according to a second modification of the first embodiment. Figure 6 This is a circuit diagram (heater mode) showing a vehicle temperature control system according to a third modified example of the first embodiment. Figure 7 This is a circuit diagram (heater mode) showing a vehicle temperature control system according to a fourth modified example of the first embodiment. Figure 8 1 is a circuit diagram showing a vehicle temperature control system according to a fifth modification of the first embodiment (dehumidification and heating) Fig. 91 is a circuit diagram showing a vehicle temperature control system according to a second embodiment (cooling mode). Fig.10 It is shown Fig. 9 A diagram of the operating state of the system when the pump fails (cooling mode). DETAILED DESCRIPTION

[0014] Hereinafter, embodiments of the present invention will be described with reference to the drawings. [First embodiment] Figure 1 The vehicle temperature control system 1 shown is installed in, for example, a vehicle not shown in the figure, such as an electric vehicle that does not have an engine but obtains the driving force for the vehicle from an electric motor for driving, or a so-called hybrid vehicle that obtains the driving force for the vehicle from an engine and an electric motor. In addition to being responsible for air conditioning functions such as heating and cooling, dehumidification, and ventilation of the cabin 8 where passengers sit, the temperature control system 1 is also responsible for thermal management and waste heat recovery of vehicle-mounted devices such as a battery device (power supply device), a driving motor, and heat-generating electronic devices mounted on the vehicle. The act of adjusting to an appropriate temperature or humidity, or managing the vehicle-mounted devices to an appropriate temperature is collectively referred to as "thermal management." The electric power stored in the vehicle-mounted battery device is supplied to the temperature control system 1 and the electric devices or electronic devices included in the vehicle-mounted devices. The vehicle-mounted battery device is charged from an external power supply when the vehicle is stopped.

[0015] 〔Overall structure〕 The temperature control system 1 comprises: a refrigerant circuit 10, which is configured to allow the refrigerant to circulate; a heat medium circuit 20, which is configured to allow the heat medium that performs heat exchange with the refrigerant to circulate; and a control device 5, which sets the temperature control system 1 to a specified operating mode and controls the operating state of the temperature control system 1 according to the operating mode. Furthermore, the temperature control system 1 includes sensors (not shown) such as a sensor that detects the temperature of the outside air and a sensor that detects the temperature of the conditioned air blown into the machine room 8 .

[0016] The temperature control system 1 has a plurality of operation modes selected by the occupant or the control device 5. In this embodiment, the cooling mode ( Figure 1 ), heat pump mode( Figure 2 ) and heater mode ( Figure 3 ).

[0017] 〔Refrigerant circuit structure〕 like Figure 1 As shown in an example of the configuration in FIG. 1 , the refrigerant circuit 10 includes a compressor 11, a condenser 12, an expansion valve 13, and an evaporator 14. In the refrigerant circuit 10, the refrigerant circulates according to a refrigeration cycle. As the refrigerant sealed in the refrigerant circuit 10, a known appropriate single refrigerant or mixed refrigerant can be used. For example, as the refrigerant of this embodiment, HFC (Hydro Fluoro Carbon: hydrofluorocarbon) refrigerants such as R410A and R32, HFO (Hydro Fluoro Olefin: hydrofluoroolefin) refrigerants such as R1234ze and R1234yf, or hydrocarbon (HC: Hydrocarbon: hydrocarbon) refrigerants such as propane and isobutane can be used. In particular, as the refrigerant of this embodiment, R1234yf is preferably used.

[0018] When the above-mentioned fluorine-based or hydrocarbon-based refrigerants are used, a subcritical refrigeration cycle is constructed in which the refrigerant pressure on the high-pressure side does not exceed the critical pressure of the refrigerant. When carbon dioxide (CO2) is used as the refrigerant, a transition critical refrigeration cycle is formed in which the refrigerant pressure on the high-pressure side exceeds the critical pressure of the refrigerant. Even in this case, the following effect can be obtained, that is, the refrigerant dissipates heat through the high-pressure side heat exchanger as in the condenser 12 of the present embodiment, and the refrigerant absorbs heat through the low-pressure side heat exchanger as in the evaporator 14 of the present embodiment, so a refrigerant that forms a transition critical refrigeration cycle such as the carbon dioxide refrigerant can also be adopted in the refrigerant circuit 10.

[0019] The compressor 11 corresponds to an electric compressor provided with a motor (not shown). The compressor 11 adiabatically compresses the refrigerant sucked into a casing (not shown) by a compression mechanism and discharges the refrigerant.

[0020] The condenser 12 exchanges heat between the refrigerant gas discharged from the compressor 11 and a heating medium. The expansion valve 13 (decompression unit) adiabatically expands the refrigerant flowing out of the condenser 12 by decompressing the refrigerant. As the expansion valve 13, a temperature-type expansion valve can be used in addition to an electronic expansion valve whose opening can be controlled according to a command from the control device 5. Alternatively, a capillary tube can be used instead of the expansion valve 13.

[0021] The evaporator 14 exchanges heat between the refrigerant flowing out of the expansion valve 13 and a heating medium. The refrigerant evaporated by the evaporator 14 is sucked into the compressor 11. An accumulator (gas-liquid separator) (not shown) may be provided between the evaporator 14 and the compressor 11 .

[0022] A relatively high refrigerant pressure (high pressure) is applied to the condenser 12, and a relatively low refrigerant pressure (low pressure) is applied to the evaporator 14. The refrigerant circulates in the refrigerant circuit 10 based on the pressure difference between the high pressure and the low pressure. exist Figure 1In FIG. 1 , the flow of the refrigerant on the low-pressure side is indicated by a thick solid line, and the flow of the refrigerant on the high-pressure side is indicated by a thick dotted line. The same applies to the other figures.

[0023] The compressor 11 , the condenser 12 , the expansion valve 13 , the evaporator 14 , and refrigerant pipes connecting these elements can be installed outside the machine room 8 .

[0024] 〔Structure of the heat carrier circuit〕 The heat medium circuit 20 is configured so that a heat medium capable of exchanging heat with the refrigerant can circulate through the condenser 12 and the evaporator 14. The heat medium is used to cool or heat at least one temperature control object. The temperature control object in this embodiment corresponds to the air in the machine room 8. The heat medium sealed in the heat medium pipe 20 is a liquid such as water or salt water that is maintained in a liquid phase and circulated in the heat medium pipe 20. Examples of the salt water include a mixed liquid of water and propylene glycol or a mixed liquid of water and ethylene glycol.

[0025] like Figure 1 As shown in an example of the structure, the heat carrier circuit 20 includes a condenser 12, an evaporator 14, a first pump 21 and a second pump 22, an outdoor heat exchanger 23, an outdoor heat exchanger bypass path 24, an indoor heat exchanger 25, a liquid storage tank 27, an on-off valve 28, and a first switching valve 31, a second switching valve 32 and a third switching valve 33 as multiple flow path switching valves.

[0026] exist Figure 1 and Figure 2 In the example shown, due to the flow rate adjustment by the condenser flow rate adjustment valve 12V, the total amount of the heat medium flowing from the first switching valve 31 toward the condenser 12 does not flow into the condenser bypass path 12A but flows into the condenser 12. In addition, due to the flow rate adjustment by the evaporator flow rate adjustment valve 14V, the total amount of the heat medium flowing from the first switching valve 31 toward the evaporator 14 does not flow into the evaporator bypass path 14A but flows into the evaporator 14.

[0027] The first pump 21 and the second pump 22 are both equivalent to electric pumps driven by a motor not shown. The first pump 21 presses the heat medium by sucking and discharging the heat medium flowing out of at least one of the evaporator 14 and the evaporator bypass path 14A. The second pump 22 presses the heat medium by sucking and discharging the heat medium flowing out of at least one of the condenser 12 and the condenser bypass path 12A.

[0028] The outdoor heat exchanger 23 exchanges heat between the outside air outside the machine room 8 and the heat medium. The outdoor heat exchanger 23 is equivalent to a radiator arranged near the air inlet of the vehicle, for example. The outside air supplied to the outdoor heat exchanger 23 by the running of the vehicle and the operation of the outdoor blower 23A dissipates or absorbs heat according to the temperature difference between the outside air and the heat medium.

[0029] The indoor heat exchanger 25 provides conditioned air to the machine room 8 by exchanging heat between the air sent by the indoor blower 25A and the heat medium. The indoor blower 25A is driven by a motor to blow the air in the machine room 8 (inside air) or outside air, or a mixed gas of inside air and outside air to the indoor heat exchanger 25. The HVAC (Heating, Ventilation, and Air Conditioning) unit U includes an indoor heat exchanger 25, an indoor blower 25A, and a duct (not shown) through which the air sent by the indoor blower 25A flows.

[0030] The heating medium circuit 20 preferably includes an indoor heat exchanger bypass path 26 for allowing the heating medium to bypass the indoor heat exchanger 25 . The temperature control system 1 includes a battery device 6 ( Figure 8 ) and other vehicle-mounted equipment, when air conditioning in the machine room 8 is not performed, the heat medium bypassing the indoor heat exchanger 25 can be supplied to the battery device 6 through the indoor heat exchanger bypass path 26.

[0031] The elements of the heat medium circuit 20 other than the indoor heat exchanger 25 , namely, the condenser 12 , the evaporator 14 , the first pump 21 , the second pump 22 , the outdoor heat exchanger 23 , the outdoor heat exchanger bypass path 24 and the first to third switching valves 31 to 33 can be arranged outside the machine room 8 .

[0032] The liquid storage tank 27 is open to the atmosphere through an atmospheric opening not shown in the figure, and stores the heat medium in an accessible manner. The liquid storage tank 27 is equivalent to a mechanism that can cope with the volume change caused by the temperature change of the heat medium, and in the first pump 21 and the second pump 22, it plays the role of keeping the suction part of at least one of the connected ones at atmospheric pressure. In the heat medium circuit 20, only one liquid storage tank 27 is provided.

[0033] When the heat medium sealed in the heat medium circuit 20 expands as the temperature rises, the liquid storage tank 27 receives the heat medium that exceeds the volume of the piping of the heat medium circuit 20 inside the tank. Also, when the volume of the heat medium decreases as the temperature drops, the heat medium is replenished from the liquid storage tank 27 to the piping of the heat medium circuit 20, so that the piping is kept filled with the heat medium. That is, the liquid storage tank 27 can prevent the internal pressure of the piping from becoming too high or the piping from becoming negative pressure. In order to achieve this effect, the liquid storage tank 27 only needs to be connected to at least one point of the heat medium circuit 20.

[0034] The liquid storage tank 27 is configured to be connectable to the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22 directly or via the communication pipe 403. The liquid storage tank 27 of this embodiment is arranged near the suction parts 21A and 22A of the pumps 21 and 22 arranged close to each other.

[0035] In addition, considering the assembly of the components of the refrigerant circuit 10 or the heating medium circuit 20, the installation space of the components in the temperature control system 1, etc., the evaporator 14 and the condenser 12 are preferably arranged symmetrically. It is preferred that the first pump 21 and the second pump 22 are also arranged symmetrically and close to each other, similar to the evaporator 14 and the condenser 12.

[0036] The liquid inlet and outlet 27A of the liquid storage tank 27 is connected to the connecting pipe 403 connecting the pipe 401 between the evaporator 14 and the first pump 21 and the pipe 402 between the condenser 12 and the second pump 22. The liquid inlet and outlet 27A is usually provided at the bottom of the liquid storage tank 27. The atmosphere opening (not shown) is formed above the maximum liquid level in the liquid storage tank 27, and is usually formed at the upper part of the liquid storage tank 27.

[0037] In this embodiment, regardless of the operation mode, the suction part 21A of the first pump 21 is connected to the liquid storage tank 27 through the connecting pipe 403. On the other hand, the suction part 22A of the second pump 22 is connected to the liquid storage tank 27 by opening the on-off valve 28 provided in the connecting pipe 403 only in the specified mode (M1, M2) according to the structure of the circuit set in the heat medium circuit 20.

[0038] The on-off valve 28 corresponds to an electromagnetic valve that is opened and closed in accordance with a control command from the control device 5. The on-off valve 28 of the present embodiment is disposed between the reservoir tank 27 and the second pump 22 in the communication pipe 403.

[0039] exist Figure 1 The cooling mode M1 and Figure 2 In the heat pump mode M2 ​​shown in FIG. 1 , since the on-off valve 28 is open, both the first pump 21 and the second pump 22 are connected to the liquid storage tank 27 (both connected state S Both ). On the other hand, Figure 3 In the heater mode M3 shown in FIG. 1 , the on-off valve 28 is closed, so the second pump 22 is not connected to the liquid storage tank 27. At this time, only the first pump 21 is connected to the liquid storage tank 27 (one connection state S One ).

[0040] That is, the on-off valve 28 is equivalent to providing one connection state S to the first pump 21 and the second pump 22. One Or the connection status of both parties S Both As a connection valve for the connection state with the liquid storage tank 27. like Figure 3 As shown in FIG. 1 , the black-painted on-off valve 28 is closed. The same is true in other figures.

[0041] The first to third switching valves 31 to 33 are all electric valves that can be controlled to open and close according to a command from the control device 5 , and are configured to be able to switch the flow path of the heating medium according to each operation mode. In the present embodiment, the first switching valve 31 and the second switching valve 32 are four-way valves, and the third switching valve 33 corresponds to a three-way valve. In order to set a path required for realizing the operation mode in the heating medium circuit 20 , the first to third switching valves 31 to 33 can be replaced with electric valves having an appropriate structure and an appropriate number.

[0042] By switching the flow of the heating medium by at least one of the first to third switching valves 31, 32, and 33, the heating medium circuit 20 is configured to be able to set the first circuit C1 and the second circuit C2 in parallel ( Figure 1 and Figure 2 ); and is configured to be able to set the series circuit CC ( Figure 3 ).

[0043] The low-pressure circuit C1 flowing out of the evaporator 14 and returning to the evaporator 14 is divided into a second circuit C2 of the heat medium flowing out of the condenser 12 and returning to the condenser 12. Hereinafter, the first circuit C1 and the second circuit C2 may be referred to as parallel circuits C1 and C2.

[0044] In the parallel circuit C1, C2 Figure 1 and Figure 2 In the figure, the flow of the relatively low-temperature heat carrier (low-temperature heat carrier) pumped by the first pump 21 and circulated in the first circuit C1 is represented by a solid line, and the flow of the relatively high-temperature heat carrier (high-temperature heat carrier) pumped by the second pump 22 and circulated in the second circuit C2 is represented by a single-dotted line. A path through which neither the low-temperature heat medium nor the high-temperature heat medium is pressure-fed (an unused path) is indicated by a dotted line.

[0045] On the other hand, the series circuit CC is equivalent to a continuous circuit including the evaporator 14 and the condenser 12 arranged in series. When setting the series circuit CC, for example, Figure 3 As shown, the heat carrier flowing out of the condenser 12 flows into the evaporator 14, and flows out of the evaporator 14 and flows into the condenser 12. At this time, the heat carrier circulates in a continuous series loop CC formed in the heat carrier loop 20, and the evaporator 14 and the condenser 12 are configured in series with respect to the flow of the heat carrier.

[0046] In the series circuit CC Figure 3In the figure, the flow of a relatively low temperature heat carrier is represented by a solid line, and the flow of a relatively high temperature heat carrier is represented by a dashed line. Figure 3 Unlike the case where the parallel circuits C1 and C2 are provided, the flow of the heat medium from the evaporator 14 to the condenser 12 is indicated by a solid line, and the flow of the heat medium from the condenser 12 to the evaporator 14 is indicated by a dashed line. This means that if the heat medium flows into the evaporator 14, the temperature of the heat medium decreases due to heat dissipation to the refrigerant, and if the heat medium flows into the condenser 12, the temperature of the heat medium increases due to heat absorption from the refrigerant.

[0047] The temperature control system 1 has a plurality of operation modes using parallel circuits C1, C2 or series circuits CC. At least in the operation modes using parallel circuits C1, C2, the first pump 21 and the second pump 22 are required. The temperature control system 1 of this embodiment operates both pumps 21 and 22 even when the series circuit CC is used. In this case, the first pump 21 and the second pump 22 are arranged in series.

[0048] [Functions of each operation mode] Hereinafter, the operation of each operation mode of the temperature control system 1 will be described. Cooling mode M1( Figure 1 ): When cooling the machine room 8 through the cooling mode M1, by switching the flow of the heat medium based on the first switching valve to the third switching valves 31 to 33, a first circuit C1 including the evaporator 14, the first pump 21 and the indoor heat exchanger 25, and a second circuit C2 including the condenser 12, the second pump 22 and the outdoor heat exchanger 23 are set in the heat medium circuit 20.

[0049] The heat medium that transfers heat to the refrigerant through the evaporator 14 is sucked in and discharged by the first pump 21, flows into the indoor heat exchanger 25 through the third switching valve 33, and cools the air blown into the machine room 8. The heat medium that has flowed out of the indoor heat exchanger 25 returns to the evaporator 14 through the first switching valve 31. On the other hand, the heat medium that absorbs heat from the refrigerant in the condenser 12 is sucked in and discharged by the second pump 22, flows into the outdoor heat exchanger 23 through the second switching valve 32, and dissipates heat to the outside air. The heat medium that flows out of the outdoor heat exchanger 23 returns to the condenser 12 through the first switching valve 31.

[0050] When the parallel circuits C1 and C2 are set, the on-off valve 28 is opened to give the first pump 21 and the second pump 22 a dual connection state S. Both . At this time, the pressure of the heat medium in the first circuit C1 rises from the atmospheric pressure P0 as the suction pressure to the predetermined discharge pressure P1 by the operation of the first pump 21. The pressure of the heat medium discharged from the first pump 21 gradually decreases due to the resistance of the piping, etc., and the flow rate increases accordingly. If the pressure of the heat medium in the first circuit C1 decreases to the atmospheric pressure P0 in the suction part 21A of the first pump 21, it rises again to the discharge pressure P1 by the operation of the first pump 21.

[0051] Similar to the first circuit C1, the pressure of the heat medium in the second circuit C2 rises from the atmospheric pressure P0 as the suction pressure to the predetermined discharge pressure P2 by the operation of the second pump 22, and then gradually decreases due to the resistance of the piping, etc. When the pressure of the heat medium drops to the atmospheric pressure P0 in the suction section 21A of the second pump 22, it rises again to the discharge pressure P2 by the operation of the second pump 22.

[0052] When the parallel circuits C1 and C2 are set, the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22 are both kept at atmospheric pressure. Therefore, a continuous flow of the heating medium from one end of the communication pipe 403 to the other end does not occur.

[0053] Furthermore, even if the internal pressure of the piping changes with the temperature of the heat medium, since the divided first circuit C1 and second circuit C2 are respectively connected to the liquid storage tank 27, the heat medium can flow into the liquid storage tank 27 from either the first circuit C1 or the second circuit C2, and can flow out from the liquid storage tank 27 to either the first circuit C1 or the second circuit C2. Therefore, the internal pressure of any piping of the first circuit C1 or the second circuit C2 is maintained at an appropriate value. In this way, for any circuit of the first circuit C1 or the second circuit C2, it is possible to prevent damage to piping components and the like due to excessive internal pressure of the piping, or prevent air from entering the piping from joints and the like due to negative pressure in the piping, thereby preventing bubbles from being generated in the heat medium.

[0054] Heat pump mode M2( Figure 2 ): The heat pump mode M2 ​​extracts heat from the outside air as a heat source to heat the interior of the machine room 8. In the heat pump mode M2, a first circuit C1 including an evaporator 14, a first pump 21, and an outdoor heat exchanger 23, and a second circuit C2 including a condenser 12, a second pump 22, and an indoor heat exchanger 25 are set in the heat medium circuit 20.

[0055] The heat medium that has transferred heat to the refrigerant in the evaporator 14 is sucked into and discharged by the first pump 21 , then absorbs heat from the outside air in the outdoor heat exchanger 23 and returns to the evaporator 14 . On the other hand, the heating medium that absorbs heat from the refrigerant in the condenser 12 is sucked in and discharged by the second pump 22 , flows into the indoor heat exchanger 25 , and heats the air blown into the machine room 8 . The heating medium that has flowed out of the indoor heat exchanger 25 returns to the condenser 12 .

[0056] When the parallel circuits C1 and C2 are set, as described above, the on-off valve 28 is opened to give the first pump 21 and the second pump 22 a dual connection state S. Both That is, since the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22 are both maintained at the atmospheric pressure P0, a continuous flow of the heating medium from one side to the other side of both ends of the communication pipe 403 is not generated. And, according to the connection status S of both parties Both The first circuit C1 and the second circuit C2 are connected to the liquid storage tank 27 respectively. Therefore, the internal pressure of any piping of the first circuit C1 and the first circuit C2 is maintained at an appropriate value through the action of the heat medium entering and exiting the liquid storage tank as the temperature changes.

[0057] Heater mode M3( Figure 3 ): Heater mode M3 is suitable for heating when the outside air temperature is low and heat cannot be absorbed from the outside air to the heating medium. Heater mode M3 avoids heat dissipation from the heating medium to the outside air, and transmits heat corresponding to the power of the compressor 11 as a heat source to the machine room 8 through the heating medium. Thus, even when the outside air temperature is significantly lower than 0°C, the heating capacity can be ensured.

[0058] In heater mode M3, a series circuit CC is provided in the heating medium circuit 20, and the first circuit C1 and the second circuit C2 are connected without being divided. At this time, the evaporator 14 and the condenser 12 are arranged in series, and the on-off valve 28 is closed (one connection state S One ).

[0059] The heat medium that absorbs heat from the refrigerant through the condenser 12, if sucked in and discharged by the second pump 22, flows into the indoor heat exchanger 25 through the third switching valve 33 to provide heating in the machine room 8. The heat medium that flows out of the indoor heat exchanger 25 flows into the evaporator 14 through the first switching valve 31. The heat medium that dissipates heat to the refrigerant through the evaporator 14, if sucked in and discharged by the first pump 21, flows into the outdoor heat exchanger bypass path 24 through the second switching valve 32 in order to avoid dissipating heat to the outside air. The heat medium that flows through the outdoor heat exchanger bypass path 24 returns to the condenser 12.

[0060] When setting the series loop CC, according to the connection status S OneWhen the suction part 21A of the first pump 21 is connected only to the liquid storage tank 27, the heat medium circulates in the series circuit CC on the evaporator 14 side and the condenser 12 side of the heat medium circuit 20. In the series circuit CC, the evaporator 14 and the condenser 12 are arranged in series, and the first pump 21 and the second pump 22 are arranged in series. In this way, the heat medium is sucked in at the atmospheric pressure P0 by the first pump 21 and discharged at the predetermined discharge pressure P1, and the pressure drops while flowing through the second switching valve 32 and the condenser 12, and is sucked in at the predetermined suction pressure P3 by the second pump 22. Then, the heat medium discharged at the predetermined discharge pressure P4 by the second pump 22 drops to the atmospheric pressure P0 through the third switching valve 33, the indoor heat exchanger 25, the first switching valve 31, and the evaporator 14, and is sucked in by the first pump 21.

[0061] When the series circuit CC is used, if the first pump 21 is set as the reference, a continuous flow is formed in which the heat medium discharged from the first pump 21 returns to the first pump 21 via the second pump 22. At this time, assuming that the on-off valve 28 is open, even if the suction parts 21A and 22A of the first and second pumps 21 and 22 are connected to the liquid storage tank 27, since the pressure loss from the discharge part of the first pump 21 to the suction part 22A of the second pump 22 is different from the pressure loss from the discharge part of the second pump 22 to the suction part 21A of the first pump 21, the pressure P5 of the suction part 21A of the first pump 21 is different from the pressure P6 of the suction part 22A of the second pump 22.

[0062] In order to prevent the movement of the heat medium due to such a pressure difference, the on-off valve 28 is closed to connect the suction part 21A of the first pump 21, which is one of the first and second pumps 21 and 22, to the liquid storage tank 27. In this way, since the first pump 21 side and the second pump 22 side are not connected via the connecting pipe 403, even if there is a pressure difference between the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22, it is possible to prevent a part of the heat medium from flowing from the condenser 12 to the second pump 22 side from the second pump 22 side to the first pump 21 side through the connecting pipe 403.

[0063] Assuming that the on-off valve 28 is open when the series circuit CC is used, a part of the flow of the heat medium from the condenser 12 toward the second pump 22 flows out to the first pump 21 side through the connecting pipe 403 having a smaller pressure loss than the original path. In this case, the heat medium detours from the indoor heat exchanger 25 or the evaporator 14 through the connecting pipe 403 and is sucked into the first pump 21, so the heating capacity is reduced. By closing the on-off valve 28 to prevent the heating medium from bypassing the indoor heat exchanger 25 and the evaporator 14, it is possible to ensure the required heating capacity.

[0064] If the shutoff valve 28 is closed when setting the series circuit CC, only the suction part 21A of the first pump 21, which is one of the first and second pumps 21 and 22, is connected to the liquid storage tank 27. However, at this time, since the heat medium circulates in one series circuit CC, it is sufficient to connect the liquid storage tank 27 at one point on the series circuit CC. In the heater mode M3 of the present embodiment, as the temperature of the heat medium changes, the heat medium flows from the suction part 21A of the first pump 21 into the liquid storage tank 27, or the heat medium flows out from the liquid storage tank 27 into the suction part 21A of the first pump 21, so that the internal pressure of the piping is maintained at an appropriate value.

[0065] If the pressure drop in the path of the heat medium from the first pump 21 to the second pump 22 is compared with the pressure drop in the path of the heat medium from the second pump 22 to the first pump 21, the latter path has a longer path length due to passing through the indoor heat exchanger 25, and has a greater pressure drop due to passing through more heat exchangers (the indoor heat exchanger 25 and the evaporator 14). Accordingly, it is desirable to avoid negative pressure in the suction part of the post pump by suppressing the pressure drop from the front pump to the rear pump of the pumps 21 and 22 arranged in series, whose suction parts are open to the atmosphere, when using the series circuit CC. For this purpose, it is preferred to provide an on-off valve 28 at a position closer to the second pump 22 than the liquid storage tank 27 in the connecting pipe 403. In this case, the front pump is equivalent to the first pump 21, and the rear pump is equivalent to the second pump 22.

[0066] Heater mode at start up: The operation mode using the series circuit CC is not limited to the heater mode M3. The temperature control system 1 may, for example, have a heater mode at startup (not shown), which assumes a situation where the temperature control system 1 is started after being stopped for a long time at a low outside air temperature. In this startup mode, the evaporator 14 and the condenser 12 are also arranged in series with respect to the flow of the heating medium. Here, unlike the heater mode M3, in order to give priority to the heating of the refrigerant over the heating in the machine room 8, the heating medium does not flow into the condenser 12, but is made to detour in the condenser bypass path 12A. Thereby, the heat dissipation of the refrigerant to the heating medium is prevented.

[0067] In the heater mode at startup, the heating medium is caused to flow into the outdoor heat exchanger 23 so that the heating medium absorbs heat from the outside air through the outdoor heat exchanger 23. Furthermore, the heating medium flowing out of the indoor heat exchanger 25 is caused to dissipate heat to the refrigerant in the evaporator 14. Furthermore, in order to suppress heat exchange between the heating medium and the air, it is preferred that the heating medium is detoured from the indoor heat exchanger 25 through the indoor heat exchanger bypass path 26, and the operation of the indoor air blower 25A is stopped.

[0068] When the temperature of the heating medium is about the same as the outside air temperature which is much lower than 0°C, immediately after the temperature control system 1 is started, the low pressure of the refrigerant circuit 10 decreases due to the refrigerant cooling the heat medium, and the evaporation temperature of the refrigerant is lower than the outside air temperature. However, according to the heater mode at startup, by continuously transferring the heat absorbed from the outside air to the heating medium to the refrigerant, the low pressure of the refrigerant circuit 10 can be gradually increased, so that the refrigerant circuit 10 can reach stable operation as soon as possible. After the heater mode at startup, it is possible to transfer to the heater mode M3.

[0069] Even in the heater mode at startup, the on-off valve 28 is closed as in the heater mode M3. Therefore, the internal pressure of the heating medium pipe is maintained at an appropriate value, and the flow of the heating medium bypassing through the connecting pipe 403 can be avoided, thereby promoting the startup of the refrigerant circuit 10.

[0070] [Main effects of this embodiment] As described above, according to the structure set in the heating medium circuit 20, the connection state of the suction parts 21A and 22A of the first and second pumps 21 and 22 and the liquid storage tank 27 can be selected by the on-off valve 28. Therefore, in the operation mode using the parallel circuits C1 and C2 and the operation mode using the series circuit CC, it is possible to avoid the internal pressure of the pipe of the heating medium from becoming too high and the pipe from becoming negative pressure, and it is possible to avoid the flow bypassing the heat exchangers 25 and 14 through the connecting pipe 403 when using the series circuit CC, thereby ensuring the heating capacity.

[0071] [First Modification of First Embodiment] like Figure 4 As shown, the on-off valve 28 may also be provided between the liquid storage tank 27 and the first pump 21, that is, on the first pump 21 side of the communicating pipe 403 that is closer to the liquid storage tank 27. If the closing valve 28 is closed in the heater mode M3, the suction part 22A of the second pump 22 is connected to the liquid storage tank 27, and the suction part 21A of the first pump 21 is not connected to the liquid storage tank 27 (one-side connection state S One ).

[0072] In the heater mode M3, the suction pressure of the second pump 22 is equivalent to the atmospheric pressure P0, and the suction pressure of the first pump 21 is equivalent to the pressure dropped from the discharge pressure of the second pump 22 due to the pipe resistance, etc. Even if there is a pressure difference between the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22, the heat medium will not flow out from the first pump 21 side to the second pump 22 side through the connecting pipe 403 because the on-off valve 28 is closed. Furthermore, since the suction portion 22A of the second pump 22 is connected to the liquid tank 27 , the heat medium can be taken in and out of the liquid tank 27 in accordance with the temperature change.

[0073] That is, similar to the above-mentioned first embodiment, it is possible to avoid a reduction in heating capacity due to bypassing of the connecting pipe 403 when the heating medium uses the series circuit CC in the heater mode M3 or the heater mode at startup, thereby ensuring the required heating capacity and maintaining the internal pressure of the heating medium pipe at an appropriate value.

[0074] [Second Modification of First Embodiment] like Figure 5 As shown, the first pump 21 may be connected to the liquid storage tank 27 via the first communication pipe 403A, and the second pump 22 may be connected to the liquid storage tank 27 via the second communication pipe 403B. The liquid storage tank 27 has liquid inlets and outlets connected to the first communication pipe 403A and the second communication pipe 403B.

[0075] The on-off valve 28 is provided in the first communication pipe 403A located on the first pump 21 side, similarly to the first modification. However, the on-off valve 28 may be provided in the second communication pipe 403B located on the second pump 22 side, similarly to the first embodiment.

[0076] The second modification can also achieve the same operations and effects as those of the first embodiment.

[0077] [Third Modification of First Embodiment] pass Figure 6 The three-way valve 28-3 shown as the connection valve can also provide the first and second pumps 21 and 22 with one connection state S one Or the connection status of both parties S Both .like Figure 6 As shown, when the blackened port of the three-way valve 28-3 is closed, Similar to the case where the on-off valve 28 of the first embodiment is closed, the suction portion 21A of the first pump 21 is connected to the liquid storage tank 27 , and the suction portion 22A of the second pump 22 is not connected to the liquid storage tank 27 . By changing the closed port of the three-way valve 28 - 3 , the suction portion 22A of the second pump 22 may be connected to the liquid storage tank 27 in the same manner as in the first modification.

[0078] The third modification can also achieve the same operations and effects as those of the first embodiment described above.

[0079] [Fourth Modification of the First Embodiment] like Figure 7 As shown, the positions of the first and second pumps 21 and 22 may be changed, and the positions of the reservoir 27 and the on-off valve 28 may be changed accordingly. The first pump 21 is provided on the pipe 404 connecting the outdoor heat exchanger 23 and the first switching valve 31, and the second pump 22 is provided on the pipe 405 connecting the indoor heat exchanger 25 and the first switching valve 31. The first pump 21 and the second pump 22 are preferably arranged close to each other with the first switching valve 31 interposed therebetween.

[0080] The tank 27 is connected to a communication pipe 403 that connects the suction portion 21A of the first pump 21 and the suction portion 22A of the second pump 22. The on-off valve 28 is provided on the communication pipe 403 on the second pump 22 side or the first pump 21 side.

[0081] Alternatively, the first pump 21 may be provided on the pipe 406 between the first switching valve 31 and the condenser 12, and the second pump 22 may be provided on the pipe 407 between the first switching valve 31 and the evaporator 14. In this case as well, the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22 may be communicated with each other through the connecting pipe, and the liquid storage tank 27 and the on-off valve 28 may be provided on the connecting pipe.

[0082] According to the fourth modification, even if the positions of the pumps 21 and 22 or the reservoir tank 27 are different, the same operation and effects as those of the first embodiment can be obtained.

[0083] [Fifth Modification of the First Embodiment] Figure 8 The temperature control system 1-5 shown includes a battery device 6 as a temperature control target and two indoor heat exchangers 25-1 and 25-2 for dehumidifying and heating in the machine room 8. The first indoor heat exchanger 25-1 is arranged upstream of the air flow, and the second indoor heat exchanger 25-2 is arranged downstream of the air flow.

[0084] exist Figure 8 In the heat pump mode M2 ​​shown, the low-temperature heat medium flowing out of the evaporator 14 is supplied to the first indoor heat exchanger 25-1, and the high-temperature heat medium flowing out of the condenser 12 is supplied to the second indoor heat exchanger 25-2. Therefore, the air sent out from the indoor blower 25A is cooled to below the dew point and dehumidified by heat exchange with the low-temperature heat medium through the first indoor heat exchanger 25-1, and then heated by heat exchange with the high-temperature heat medium through the second indoor heat exchanger 25-2, and then blown into the machine room 8.

[0085] Although not specifically shown in the drawings, the battery device 6 includes a battery body as a battery, and a battery heat exchanger or a heat dissipating member provided in the battery body as necessary. The heating medium circuit 20 includes heat exchange paths 414 and 415 configured to enable the battery device 6 and the heating medium to exchange heat directly or indirectly via air or the like, and battery switching valves 34 and 35 as four-way valves that switch between opening and closing corresponding to the heat exchange paths 414 and 415, respectively.

[0086] In the heat pump mode M2 ​​, for example, the low-temperature heat medium flowing out of the first indoor heat exchanger 25 - 1 can be supplied from the first battery switching valve 34 to the battery device 6 through the first heat exchange path 414 . Although the heater mode M3 of the fifth modification is omitted in the illustration, in the heater mode M3 , the high-temperature heating medium flowing out of the second indoor heat exchanger 25 - 2 can be supplied from the first battery switching valve 34 to the battery device 6 through the first heat exchange path 414 .

[0087] The fifth modification can also achieve the same operations and effects as those of the first embodiment described above.

[0088] [Second embodiment] Next, refer to Fig. 9 and Fig.10 Next, a second embodiment of the present invention will be described. The temperature control system 2 of the second embodiment includes a refrigerant heat exchanger 14 - 2 on the indoor side, and the refrigerant circulating in the refrigerant circuit 10 is supplied thereto.

[0089] Similar to the refrigerant circuit 10 of the first embodiment, the refrigerant circuit 10-2 of the temperature control system 2 includes: a first refrigerant circuit R1 configured so that the refrigerant can circulate through the compressor 11, the condenser 12, the first expansion valve 13-1 as the first decompression section, and the evaporator 14-1; and a second refrigerant circuit R2 configured so that the refrigerant can circulate through the compressor 11, the condenser 12, the second expansion valve 13-2 as the second decompression section, and the refrigerant heat exchanger 14-2 as the evaporator. The refrigerant heat exchanger 14-2 exchanges heat between the refrigerant and the air.

[0090] The first refrigerant circuit R1 and the second refrigerant circuit R2 can each independently form a refrigeration cycle. When both the first refrigerant circuit R1 and the second refrigerant circuit R2 are used simultaneously, the expansion valves and evaporators of the first refrigerant circuit R1 and the second refrigerant circuit R2 are connected in parallel. The second refrigerant circuit R2 includes a pipe 501 connected to the refrigerant outflow side of the condenser 12 and a pipe 502 connected to the refrigerant discharge side of the evaporator 14 .

[0091] According to the temperature control system 2 , similarly to the temperature control systems of the first embodiment and its modified example, it is possible to realize a cooling mode, a dehumidification and heating mode, a heat pump mode, a heater mode, a startup heater mode, etc. Here, the cooling mode M1 is exemplified.

[0092] The heating medium circuit 20 included in the temperature control system 2 has substantially the same structure as the heating medium circuit 20 of the first embodiment. However, the second switching valve 32 is changed from a four-way valve to a three-way valve.

[0093] The refrigerant heat exchanger 14-2 is arranged on the upstream side of the air flow generated by the indoor air-sending fan 25A that sends air to the refrigerant heat exchanger 14-2 and the indoor heat exchanger 25. The indoor heat exchanger 25 is arranged on the downstream side of the air flow.

[0094] In the cooling mode M1 or the heat pump mode (not shown), the heating medium circuit 20 is set to have: the first circuit C1 of the heating medium flows out of the evaporator 14 and then flows into the evaporator 14; and the second circuit C2 of the heating medium flows out of the condenser 12 and then flows into the condenser 12. However, in a mode including a part of the cooling mode M1, the first circuit C1 is not used. Therefore, the operation of the first pump 21 that pressurizes the heating medium of the first circuit C1 is stopped.

[0095] In the heater mode or the startup heater mode (not shown), a series circuit CC including the condenser 12 and the evaporator 14 arranged in series is set in the heating medium circuit 20 .

[0096] Below, reference Fig. 9 The flows of the refrigerant and the heating medium are described. The cooling mode M1 uses only the second refrigerant circuit R2 of the first refrigerant circuit R1 and the second refrigerant circuit R2. Therefore, the first expansion valve 13-1 of the first refrigerant circuit R1 is closed. In the cooling mode M1, only the second circuit C2 (used circuit) is used, and the first circuit C1 (unused circuit) is not used. Therefore, the operation of the first pump 21 for pumping the heat medium in the first circuit C1 is stopped.

[0097] Since the parallel circuits C1 and C2 are provided in the heat medium circuit 20, the on-off valve 28 is opened. That is, the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22 are connected to the liquid storage tank 27 (both connection states S Both ). Regardless of whether the pumps 21 and 22 are working, the first and second circuits C1 and C2 are connected to the liquid storage tank 27, so the internal pressure of the heat medium piping is maintained at an appropriate value. In addition, the suction part 21A of the first pump 21 and the suction part 22A of the second pump 22 are both maintained at atmospheric pressure, so the heat medium does not flow in the connecting piping 403.

[0098] The flow of the refrigerant in the second refrigerant circuit R2 is described. The refrigerant gas sucked into the compressor 11 is adiabatically compressed and discharged by the compressor 11, and is liquefied by heat exchange with the heat medium in the condenser 12. Furthermore, the refrigerant flows into the second expansion valve 13-2 through the piping 501, and adiabatically expands by the decompression based on the second expansion valve 13-2, and the refrigerant with a reduced temperature flows into the refrigerant heat exchanger 14-2. The refrigerant flowing in the refrigerant heat exchanger 14-2 cools the air delivered from the indoor air blower 25A, thereby cooling the machine room 8. The refrigerant leaving the refrigerant heat exchanger 14-2 flows through the piping 502 and is sucked into the compressor 11.

[0099] As the flow of the heating medium, the heating medium of the second circuit C2 transfers heat received from the refrigerant in the condenser 12 to the outdoor heat exchanger 23. The heating medium having transferred heat to the outside air in the outdoor heat exchanger 23 returns to the condenser 12 via the first switching valve 31.

[0100] According to the cooling mode M1 of the temperature control system 2, the temperature control object can be directly cooled without passing through a heat medium by the refrigerant supplied to the refrigerant heat exchanger 14-2 as an evaporator as a cold heat source. Therefore, the cooling capacity can be improved, and the followability of the control relative to the temperature change of the temperature control object or the outside air can also be improved.

[0101] Fig.10 The diagram shows a case where the operation in the cooling mode M1 is continued by operating the first pump 21 corresponding to the first circuit C1 (unused circuit) when the second pump 22 corresponding to the second circuit C2 (used section) stops due to a failure. For example, if the control device 5 detects that the second pump 22 has failed based on the refrigerant pressure measurement value, the control device 5 operates the first pump 21 through a control command. Fig.10 As shown, the suction part 21A of the failed first pump 21 is connected to the suction part 22A of the second pump 22 via the connecting pipe 403, so that the heat medium pumped by the first pump 21 circulates in the outdoor heat exchanger 23 and the condenser 12. At this time, the connecting path 403 and a part of the first circuit C1 are assembled in the second circuit C2.

[0102] As the heat medium pressure delivery mechanism in the cooling mode M1 of the second embodiment, the second pump 22 can be replaced by the first pump 21, and the first pump 21 can also be replaced by the second pump 22. Fig.10 As shown, when the first pump 21 is operated to implement the cooling mode M1, if the first pump 21 fails, Fig. 9 As shown, the cooling mode M1 can be continued by operating the second pump 22 .

[0103] Not limited to the cooling mode M1, when any of the first and second pumps 21 and 22 is arranged in the unused section of the heating medium circuit 20, that is, when only one of the first circuits C1 and C2 is used, the same pump replacement as described above can be performed.

[0104] In addition to the above, the structures listed in the above embodiments may be selected or replaced, or may be appropriately changed to other structures.

[0105] [Note] Through the above disclosure, the structure described below is understood. [1] A temperature control system for a vehicle, comprising: The refrigerant circuit 10 includes a compressor 11, a high-pressure side heat exchanger 12, a pressure reducing unit 13, and a low-pressure side heat exchanger 14, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heating medium circuit (20) is configured to circulate a heating medium for exchanging heat with the refrigerant. The heat carrier circuit 20 has: The high-pressure side heat exchanger 12 enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger 14 enables the refrigerant to exchange heat with the heat carrier; The first pump 21 and the second pump 22 are configured to be able to pressure-transport the heat medium; The outdoor heat exchanger 23 allows the external air to exchange heat with the heat carrier; The temperature control device 25 is equivalent to the temperature control object heated or cooled by the heat carrier, or is used to heat or cool the temperature control object; a liquid storage tank 27 capable of storing the heat medium and configured to be connectable to the respective suction parts 21A and 22A of the first pump 21 and the second pump 22; and The connection valve 28 is configured to provide the first pump 21 and the second pump 22 with a connection state S1. One And the connection status S of both parties connected Both Any connection state in is used as the connection state with the liquid storage tank 27, The heat carrier circuit 20 is constructed as follows: The first circuit C1 including the low-pressure side heat exchanger 14 and corresponding to the first pump 21 and the second circuit C2 including the high-pressure side heat exchanger 12 and corresponding to the second pump 22 can be set in parallel; Furthermore, the structure is such that a series circuit including the low-pressure side heat exchanger 14 and the high-pressure side heat exchanger 12 arranged in series and corresponding to the first pump 21 and the second pump 22 can be set.

[0106] [2] The vehicle temperature control system according to [1], wherein: The connection valve 28 is configured to provide the first pump 21 and the second pump 22 with the dual connection state S when the first circuit C1 and the second circuit C2 are set. Both , when the series circuit CC is set, the connection state S can be given to the one party One .

[0107] [3] The vehicle temperature control system according to [1] or [2], comprising: an outdoor heat exchanger bypass path 24 for allowing the heat medium to bypass the outdoor heat exchanger; and As an operation mode using the series circuit CC, With the compressor heat source mode M3, the heat medium flowing out of the high-pressure side heat exchanger 12 flows into the low-pressure side heat exchanger 14 via the temperature control device 25, and then flows into the high-pressure side heat exchanger 12 through the outdoor heat exchanger bypass path 24.

[0108] [4] A vehicle temperature control system according to any one of [1] to [3], wherein: The connection valve 28 corresponds to an on-off valve 28 provided between the suction portion 22A of the second pump 22 and the liquid inlet and outlet portion 27A of the liquid storage tank 27 .

[0109] [5] A vehicle temperature control system according to any one of [1] to [3], wherein: The connection valve 28 corresponds to an on-off valve 28 provided between the suction portion 21A of the first pump 21 and the liquid inlet and outlet portion 27A of the liquid storage tank 27 .

[0110] [6] A vehicle temperature control system according to any one of [1] to [3], wherein: The connection valve 28 - 3 corresponds to the three-way valve 28 - 3 corresponding to the suction portion 21A of the first pump 21 , the suction portion 22A of the second pump 22 , and the liquid inlet and outlet portion 27A of the liquid storage tank 27 .

[0111] [7] The vehicle temperature control system according to any one of [1] to [6], comprising: An operation mode in which only one of the first circuit C1 and the second circuit C2 is used, In the operation mode, one of the first circuit C1 and the second circuit C2 is a used circuit and the other is a non-used circuit, and the first pump 21 and the second pump 22 are given the dual connection state S Both , In the operation mode, when one of the first pump 21 and the second pump 22 corresponding to the use circuit fails, the other pump corresponding to the unused circuit is operated, so that a connecting path 403 connecting the suction parts 21A, 22A of the first pump 21 and the second pump 22 respectively to the liquid storage tank 27 and a part of the unused circuit are assembled in the use circuit.

[0112] [8] A temperature control method for a vehicle, which is a temperature control method using a temperature control system for a vehicle, wherein: The temperature control system has: The refrigerant circuit 10 includes a compressor 11, a high-pressure side heat exchanger 12, a pressure reducing unit 13, and a low-pressure side heat exchanger 14, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heating medium circuit (20) is configured to circulate a heating medium for exchanging heat with the refrigerant. The heat carrier circuit 20 has: The high-pressure side heat exchanger 12 enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger 14 enables the refrigerant to exchange heat with the heat carrier; The first pump 21 and the second pump 22 are configured to be able to pressure-transport the heat medium; An outdoor heat exchanger is used to exchange heat between the external air and the heat carrier; The temperature control device 25 is equivalent to the temperature control object heated or cooled by the heat carrier, or is used to heat or cool the temperature control object; a liquid storage tank 27 capable of storing the heat medium and configured to be connectable to the respective suction parts 21A and 22A of the first pump 21 and the second pump 22; and The connection valve 28 is configured to provide the first pump 21 and the second pump 22 with a connection state S1. One And the connection status S of both parties connected Both Any connection state in is used as the connection state with the liquid storage tank 27, The heat medium circuit 20 is configured such that a first circuit C1 including the low-pressure side heat exchanger 14 and corresponding to the first pump 21 and a second circuit C2 including the high-pressure side heat exchanger 12 and corresponding to the second pump 22 can be set in parallel; and a series circuit including the low-pressure side heat exchanger 14 and the high-pressure side heat exchanger 12 arranged in series and corresponding to the first pump 21 and the second pump 22 can be set, In the temperature control method, when the first circuit C1 and the second circuit C2 are set, the first pump 21 and the second pump 22 are given the dual connection state S by the connection valve 28. Both When the series circuit CC is set, the first pump 21 and the second pump 22 are given the connection state S by the connecting valve 28. One . Explanation of symbols

[0113] 1, 1-5, 2-temperature control system (temperature control system for vehicle), 5-control device, 6-battery device, 8-machine room, 10, 10-2-refrigerant circuit, 11-compressor, 12-condenser (high-pressure side heat exchanger), 12A-condenser bypass path, 12V-condenser flow control valve, 13-expansion valve (pressure reducing part), 14, 14-1-evaporator (low-pressure side heat exchanger), 14-2-refrigerant heat exchanger, 14A-evaporator bypass path, 14V-evaporator flow control valve, 20-heat medium circuit, 21-first pump, 21A-suction part, 22-second pump, 22A-suction part, 23-outdoor heat exchanger, 23A-outdoor fan, 24-outdoor heat exchanger bypass path, 25-indoor heat exchanger, 25A-indoor fan, 26-indoor heat exchanger 1-1 heat exchanger bypass path, 27-liquid storage tank, 27A-liquid inlet and outlet (liquid inlet and outlet part), 28-opening and closing valve (connecting valve), 28-3-three-way valve (connecting valve), 31-first switching valve, 32-second switching valve, 33-third switching valve, 34-first battery switching valve, 35-second battery switching valve, 401, 402, 404-407-piping, 403-connecting piping (connecting path), 403A-first connecting piping, 403B-second connecting piping, 414-first heat exchange path, 415-second heat exchange path, 501, 502-piping, C1-first circuit, C2-second circuit, CC-series circuit, M1-cooling mode, M2-heat pump mode, M3-heater mode, R1-first refrigerant circuit, R2-second refrigerant circuit, S One -Party connection status, S Both -Both parties connected, U-HVAC unit.

Claims

1. A temperature control system for a vehicle, comprising: A refrigerant circuit includes a compressor, a high-pressure side heat exchanger, a pressure reducing unit, and a low-pressure side heat exchanger, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heat medium circuit is configured to circulate a heat medium for exchanging heat with the refrigerant. The heat carrier circuit has: The high-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; The first pump and the second pump are configured to pressure-transport the heat medium; An outdoor heat exchanger is used to exchange heat between the external air and the heat carrier; The temperature control device is equivalent to the temperature control object heated or cooled by the heat carrier, or is used to heat or cool the temperature control object; a liquid storage tank capable of storing the heat medium and configured to be connectable to the respective suction parts of the first pump and the second pump; and a connection valve configured to provide the first pump and the second pump with either a one-way connection state or a two-way connection state as a connection state with the liquid storage tank, The heat carrier circuit is composed of: A first circuit including the low-pressure side heat exchanger and corresponding to the first pump and a second circuit including the high-pressure side heat exchanger and corresponding to the second pump can be set in parallel; Furthermore, the structure is such that a series circuit including the low-pressure side heat exchanger and the high-pressure side heat exchanger arranged in series and corresponding to the first pump and the second pump can be set.

2. The vehicle temperature control system according to claim 1, wherein: The connection valve is configured to provide the first pump and the second pump with the both connection states when the first circuit and the second circuit are set, and to provide the one connection state when the series circuit is set.

3. The vehicle temperature control system according to claim 1 or 2, comprising: an outdoor heat exchanger bypass path for allowing the heat medium to bypass the outdoor heat exchanger; and As an operation mode using the series circuit, The heat medium having a compressor heat source mode flows out of the high-pressure side heat exchanger into the low-pressure side heat exchanger via the temperature control device, and then flows into the high-pressure side heat exchanger via the outdoor heat exchanger bypass path.

4. The vehicle temperature control system according to claim 1 or 2, wherein: The connection valve corresponds to an on-off valve provided between the suction portion of the second pump and the liquid inlet and outlet portion of the liquid storage tank.

5. The vehicle temperature control system according to claim 1 or 2, wherein: The connection valve corresponds to an on-off valve provided between the suction portion of the first pump and the liquid inlet and outlet portion of the liquid storage tank.

6. The vehicle temperature control system according to claim 1 or 2, wherein: The connection valve corresponds to a three-way valve corresponding to the suction portion of the first pump, the suction portion of the second pump, and the liquid inlet and outlet portion of the liquid storage tank.

7. The vehicle temperature control system according to claim 1 or 2, comprising: An operation mode using only one of the first circuit and the second circuit, In the operation mode, one of the first circuit and the second circuit is a used circuit and the other is a non-used circuit, and the first pump and the second pump are both connected. In the operation mode, when one of the first pump and the second pump corresponding to the use circuit fails, the other pump corresponding to the unused circuit is operated, so that a connecting path connecting the suction parts of each of the first pump and the second pump to the liquid storage tank and a part of the unused circuit are assembled in the use circuit.

8. A temperature control method for a vehicle, which is a temperature control method using a temperature control system for a vehicle, wherein: The temperature control system has: A refrigerant circuit includes a compressor, a high-pressure side heat exchanger, a pressure reducing unit, and a low-pressure side heat exchanger, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heat medium circuit is configured to circulate a heat medium for exchanging heat with the refrigerant. The heat carrier circuit has: The high-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; The first pump and the second pump are configured to pressure-transport the heat medium; An outdoor heat exchanger is used to exchange heat between the external air and the heat carrier; The temperature control device is equivalent to the temperature control object heated or cooled by the heat carrier, or is used to heat or cool the temperature control object; a liquid storage tank capable of storing the heat medium and configured to be connectable to the respective suction parts of the first pump and the second pump; and a connection valve configured to provide the first pump and the second pump with either a one-way connection state or a two-way connection state as a connection state with the liquid storage tank, The heat carrier circuit is composed of: A first circuit including the low-pressure side heat exchanger and corresponding to the first pump and a second circuit including the high-pressure side heat exchanger and corresponding to the second pump can be set in parallel; The invention is configured to be able to set a series circuit including the low-pressure side heat exchanger and the high-pressure side heat exchanger arranged in series and corresponding to the first pump and the second pump, In the temperature control method, when the first circuit and the second circuit are set, the first pump and the second pump are given the two-way connection state through the connecting valve; when the series circuit is set, the first pump and the second pump are given the one-way connection state through the connecting valve.

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