Thermal management system, thermal management system control method and vehicle

Abstract

The invention provides a heat management system, a heat management system control method and a vehicle, the heat management system comprises a heat regenerator and a compressor, and the heat regenerator communicates with the compressor; a refrigerant loop of the heat management system comprises a first refrigerant loop corresponding to a heating mode and a second refrigerant loop corresponding to a refrigerating mode of the heat management system. The first refrigerant loop is used for reducing the heat exchange power of the heat regenerator; and the second refrigerant loop is used for increasing the heat exchange power of the heat regenerator. The refrigeration performance of the heat management system can be improved while liquid impact of the compressor is avoided.

Description

Technical Field

[0001] The present application relates to the field of vehicle thermal management, and more specifically, to a thermal management system, a thermal management system control method, and a vehicle. Background Art

[0002] At present, the existing thermal management system adopts the following two solutions to avoid compressor liquid hammer. Among them, the first solution is to set a gas-liquid separator in front of the compressor. Although this method can greatly improve the dryness of the compressor inlet and thus avoid compressor liquid hammer, the addition of the gas-liquid separator makes the flow resistance on the low-pressure side larger, which limits the refrigeration performance of the system.

[0003] The second solution is to install a coaxial tube in front of the compressor. Although this method can increase the compressor suction superheat and avoid compressor liquid hammer, it will affect the heating and cooling performance of the system. If the power of the coaxial tube is too large, it will reduce the heating performance and efficiency of the system under low-temperature heat pump conditions. If the power of the coaxial tube is too small, it will not be conducive to improving the cooling performance of the system.

[0004] In summary, the solutions adopted by the existing thermal management system to avoid compressor liquid hammer cannot take into account both the cooling performance and heating performance of the thermal management system while avoiding compressor liquid hammer. Summary of the invention

[0005] The purpose of the embodiments of the present application is to provide a thermal management system, a thermal management system control method and a vehicle, so as to improve the cooling performance of the thermal management system while avoiding compressor liquid hammer.

[0006] In a first aspect, the present invention provides a thermal management system, the thermal management system comprising a regenerator and a compressor, the regenerator being in communication with the compressor;

[0007] The refrigerant circuit of the thermal management system comprises a first refrigerant circuit corresponding to a heating mode, and a second refrigerant circuit corresponding to a cooling mode of the thermal management system;

[0008] The first refrigerant circuit is used to reduce the heat exchange power of the regenerator;

[0009] The second refrigerant circuit is used to increase the heat exchange capacity of the regenerator.

[0010] The heat management system according to the first aspect of the present application uses two refrigerant circuits, namely the first refrigerant circuit and the second refrigerant circuit. In the heating mode, the first refrigerant circuit is adopted, and in the cooling mode, the second refrigerant circuit is adopted. Furthermore, in the heating mode, the first refrigerant circuit is used to reduce the heat exchange power of the regenerator, thereby reducing the heat of the low-temperature and low-pressure refrigerant transferred to the compressor inlet, making the subcooling degree of the liquid refrigerant at the outlet of the regenerator moderate and the superheat degree of the refrigerant at the compressor inlet small, mainly playing the role of ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor. On the other hand, in the cooling mode, the second refrigerant circuit is used to increase the heat exchange power of the regenerator, thereby increasing the subcooling degree of the liquid refrigerant at the outlet of the liquid receiver dryer and increasing the superheat degree of the refrigerant at the compressor inlet, improving the refrigeration performance of the system.

[0011] In an alternative embodiment, the number of times the first refrigerant circuit flows through the regenerator is one.

[0012] In this alternative embodiment, through the first refrigerant circuit, the refrigerant can pass through the regenerator only once, thereby reducing the heat of the low-temperature and low-pressure refrigerant transferred to the compressor inlet, making the subcooling degree of the liquid refrigerant at the outlet of the regenerator moderate and the superheat degree of the refrigerant at the compressor inlet small, mainly playing the role of ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor, and ensuring high energy efficiency of the heat pump heating function.

[0013] In an alternative embodiment, the number of times the second refrigerant circuit flows through the regenerator is multiple.

[0014] In this alternative embodiment, through the second refrigerant circuit, the refrigerant can pass through the regenerator multiple times. Furthermore, as the refrigerant passes through the regenerator multiple times, more heat will be transferred to the low-temperature and low-pressure refrigerant at the compressor inlet, increasing the subcooling degree of the liquid refrigerant at the outlet of the liquid receiver dryer and increasing the superheat degree of the refrigerant at the compressor inlet, improving the refrigeration performance of the system.

[0015] In an alternative embodiment, the heat management system further includes a liquid receiver dryer, and the liquid receiver dryer is connected to the regenerator.

[0016] In this alternative embodiment, the refrigerant can be stored through the liquid receiver dryer, and the refrigerant entering the liquid receiver dryer can be separated into liquid and gas.

[0017] In an alternative embodiment, the heat management system further includes a proportional valve, an indoor condenser, and a front cabin heat exchanger;

[0018] The proportional valve is connected to the compressor and is also connected to the front cabin heat exchanger and the indoor condenser.

[0019] In this alternative embodiment, the proportional valve can be used to distribute the flow rate ratio of the refrigerant entering the indoor condenser and the front cabin heat exchanger.

[0020] In an alternative embodiment, the thermal management system further includes a first check valve, and the first check valve is communicated with the liquid storage and dryer.

[0021] In this alternative embodiment, the refrigerant flowing out of the indoor condenser can flow unidirectionally into the liquid storage and dryer through the first check valve.

[0022] In an alternative embodiment, the thermal management system further includes a second check valve, and the second check valve is communicated with the liquid storage and dryer.

[0023] In this alternative embodiment, the refrigerant flowing out of the regenerator can flow unidirectionally into the liquid storage and dryer through the second check valve.

[0024] In an alternative embodiment, the thermal management system further includes a third check valve and an indoor evaporator. The third check valve is communicated with the regenerator and is also communicated with the indoor evaporator.

[0025] In this alternative embodiment, the refrigerant flowing out of the indoor evaporator can flow unidirectionally into the regenerator through the third check valve.

[0026] In a second aspect, the present invention provides a method for controlling a thermal management system. The method for controlling the thermal management system is applied to the thermal management system according to any one of the foregoing embodiments. The method for controlling the thermal management system includes:

[0027] Obtaining the operating mode of the thermal management system;

[0028] When the operating mode of the thermal management system is the heating mode, the first refrigerant circuit is opened so that the refrigerant of the thermal management system flows along the first refrigerant circuit;

[0029] When the operating mode of the thermal management system is the cooling mode, the second refrigerant circuit is opened so that the refrigerant of the thermal management system flows along the second refrigerant circuit.

[0030] The method of the second aspect of the present application can obtain the operating mode of the thermal management system. Furthermore, when the operating mode of the thermal management system is the heating mode, the first refrigerant circuit can be opened so that the refrigerant of the thermal management system flows along the first refrigerant circuit. And when the operating mode of the thermal management system is the cooling mode, the second refrigerant circuit can be opened so that the refrigerant of the thermal management system flows along the second refrigerant circuit. Thus, in the heating mode, the heat exchange power of the regenerator can be reduced by using the first refrigerant circuit, and further the heat transferred to the low-temperature and low-pressure refrigerant at the compressor inlet can be reduced, so that the supercooling degree of the liquid refrigerant at the regenerator outlet is moderate and the superheat degree of the refrigerant at the compressor inlet is small, which mainly plays a role in ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor. On the other hand, in the cooling mode, the heat exchange power of the regenerator can be increased by using the second refrigerant circuit, and further the supercooling degree of the liquid refrigerant at the outlet of the liquid receiver dryer can be increased and the superheat degree of the refrigerant at the compressor inlet can be increased, thereby improving the refrigeration performance of the system.

[0031] In a third aspect, the present invention provides a vehicle, which includes the thermal management system according to any one of the foregoing embodiments.

[0032] The vehicle of the third aspect of the present application can, in the heating mode, reduce the heat exchange power of the regenerator by using the first refrigerant circuit, and further reduce the heat transferred to the low-temperature and low-pressure refrigerant at the compressor inlet, so that the supercooling degree of the liquid refrigerant at the regenerator outlet is moderate and the superheat degree of the refrigerant at the compressor inlet is small, which mainly plays a role in ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor. On the other hand, in the cooling mode, the heat exchange power of the regenerator can be increased by using the second refrigerant circuit, and further the supercooling degree of the liquid refrigerant at the outlet of the liquid receiver dryer can be increased and the superheat degree of the refrigerant at the compressor inlet can be increased, thereby improving the refrigeration performance of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments of the present application will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present application, and thus should not be regarded as limiting the scope. For those of ordinary skill in the art, other related drawings can be obtained based on these drawings without creative efforts.

[0034] Figure 1 is a schematic framework diagram of the first thermal management system provided by the embodiment of the present application;

[0035] Figure 2 is a schematic framework diagram of the second thermal management system provided by the embodiment of the present application;

[0036] Figure 3 is a schematic framework diagram of the third thermal management system provided by the embodiment of the present application;

[0037] Figure 4 It is a schematic diagram of the framework of the fourth thermal management system provided by the embodiments of the present application;

[0038] Figure 5 It is a schematic flowchart of a method for controlling a thermal management system provided by the embodiments of the present application.

[0039] Icons: Compressor 101, regenerator 102, liquid receiver / dryer 103. Detailed implementation manners

[0040] Next, the technical solutions in the embodiments of the present application will be described with reference to the accompanying drawings in the embodiments of the present application.

[0041] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the technical field to which this application belongs; the terms used herein are only for the purpose of describing specific embodiments and are not intended to limit this application; the terms "including" and "having" and any variations thereof in the specification and claims of this application and the above drawings are intended to cover non-exclusive inclusion.

[0042] In the description of the embodiments of the present application, technical terms such as "first" and "second" are only used to distinguish different objects and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity, specific order or primary-secondary relationship of the indicated technical features. In the description of the embodiments of the present application, "a plurality of" means two or more unless otherwise specifically defined.

[0043] Referring to "embodiments" herein means that the specific features, structures or characteristics described in connection with the embodiments may be included in at least one embodiment of this application. The phrase appears in various places in the specification and does not necessarily refer to the same embodiment, nor is it an independent or alternative embodiment mutually exclusive with other embodiments. Those skilled in the art explicitly and implicitly understand that the embodiments described herein may be combined with other embodiments.

[0044] In the description of the embodiments of the present application, the term "and / or" is only a description of the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B may represent: A exists alone, A and B exist simultaneously, and B exists alone. In addition, the character " / " in this article generally represents an "or" relationship between the associated objects before and after.

[0045] In the description of the embodiments of the present application, the term "multiple times" means more than two times.

[0046] At present, the existing thermal management system adopts the following two solutions to avoid compressor liquid hammer. Among them, the first solution is to set a gas-liquid separator in front of the compressor. Although this method can greatly improve the dryness of the compressor inlet and thus avoid compressor liquid hammer, the addition of the gas-liquid separator makes the flow resistance on the low-pressure side larger, which limits the refrigeration performance of the system.

[0047] The second solution is to install a coaxial tube in front of the compressor. Although this method can increase the compressor suction superheat and avoid compressor liquid hammer, it will affect the heating and cooling performance of the system. If the power of the coaxial tube is too large, it will reduce the heating performance and efficiency of the system under low-temperature heat pump conditions. If the power of the coaxial tube is too small, it will not be conducive to improving the cooling performance of the system.

[0048] In summary, the solutions adopted by the existing thermal management system to avoid compressor liquid hammer cannot take into account both the cooling performance and heating performance of the thermal management system while avoiding compressor liquid hammer.

[0049] In response to the above technical problems, the present application provides a thermal management system, which can use the first refrigerant circuit to reduce the heat exchange power of the regenerator in the heating mode, thereby reducing the heat of the low-temperature and low-pressure refrigerant transferred to the compressor inlet, so that the subcooling degree of the liquid refrigerant at the outlet of the regenerator is moderate and the superheat degree of the refrigerant at the inlet of the compressor is small, which mainly plays the role of ensuring the dryness of the refrigerant at the inlet of the compressor to avoid liquid hammer of the compressor. On the other hand, in the cooling mode, the second refrigerant circuit is used to increase the heat exchange power of the regenerator, thereby increasing the subcooling degree of the liquid refrigerant at the outlet of the liquid storage drying tank and increasing the superheat degree of the refrigerant at the inlet of the compressor, thereby improving the refrigeration performance of the system.

[0050] See also Figure 1 , Figure 1 Schematic diagram of the framework of the first thermal management system provided by the embodiment of the present application. Figure 1 As shown, the thermal management system of the embodiment of the present application includes a heat regenerator 102 and a compressor 101, the heat regenerator 102 is connected to the compressor 101, and the refrigerant circuit of the thermal management system includes a first refrigerant circuit B corresponding to a heating mode, and a second refrigerant circuit A corresponding to a cooling mode of the thermal management system, wherein the first refrigerant circuit is used to reduce the heat exchange power of the heat regenerator, and the second refrigerant circuit is used to increase the heat exchange power of the heat regenerator.

[0051] The thermal management system according to the embodiment of the present application uses two refrigerant circuits, namely the first refrigerant circuit and the second refrigerant circuit. In the heating mode, the first refrigerant circuit is adopted, and in the cooling mode, the second refrigerant circuit is adopted. Further, in the heating mode, the first refrigerant circuit is used to reduce the heat exchange power of the regenerator, thereby reducing the heat of the low-temperature and low-pressure refrigerant transferred to the compressor inlet, making the supercooling degree of the liquid refrigerant at the outlet of the regenerator moderate and the superheat degree of the refrigerant at the compressor inlet small, mainly playing a role in ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor. On the other hand, in the cooling mode, the second refrigerant circuit is used to increase the heat exchange power of the regenerator, thereby increasing the supercooling degree of the liquid refrigerant at the outlet of the liquid receiver / dryer and increasing the superheat degree of the refrigerant at the compressor inlet, improving the refrigeration performance of the system.

[0052] In the embodiment of the present application, the regenerator is a device for realizing heat exchange between high-pressure refrigerant and low-pressure refrigerant. The compressor compresses the refrigerant and pushes the refrigerant to flow in the system, and is the core component of the air-conditioning system. Further, the refrigerant in the embodiment of the present application can also be referred to as refrigerant.

[0053] In the embodiment of the present application, the refrigerant circuit refers to the circulation path of the refrigerant in the thermal management system. Among them, according to the difference in the path, the refrigerant circuit in the embodiment of the present application can be divided into the first refrigerant circuit and the second refrigerant circuit. It should be noted that the refrigerant circuit can flow through multiple components in the thermal management system. For example, it passes through the compressor, the regenerator, and the liquid receiver / dryer. On the other hand, the first refrigerant circuit and the second refrigerant circuit can pass through the same thermal management component.

[0054] In the embodiment of the present application, both the cooling mode and the heating mode are working modes of the thermal management system. Among them, it should be noted that the cooling mode can be a pure cooling mode, or a composite mode including a cooling function such as a cooling and dehumidification mode. The heating mode can be a pure heating mode, or a composite mode including a heating function such as a heating and dehumidification mode.

[0055] In the embodiment of the present application, as an optional implementation manner, the number of times the first refrigerant circuit flows through the regenerator is one.

[0056] This optional implementation manner enables the refrigerant to pass through the regenerator only once through the first refrigerant circuit, thereby reducing the heat of the low-temperature and low-pressure refrigerant transferred to the compressor inlet, making the supercooling degree of the liquid refrigerant at the outlet of the regenerator moderate and the superheat degree of the refrigerant at the compressor inlet small, mainly playing a role in ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor, and ensuring high energy efficiency of the heat pump heating function.

[0057] In the embodiment of the present application, as an optional implementation manner, the number of times the second refrigerant circuit flows through the regenerator is multiple.

[0058] In this optional embodiment, through the second refrigerant circuit, the refrigerant can pass through the regenerator multiple times. Consequently, as the refrigerant passes through the regenerator multiple times, more heat is transferred to the low-temperature and low-pressure refrigerant at the compressor inlet, increasing the subcooling degree of the liquid refrigerant at the outlet of the liquid receiver / dryer and raising the superheat degree of the refrigerant at the compressor inlet, thereby enhancing the refrigeration performance of the system.

[0059] For this optional embodiment, the number of times the second refrigerant circuit flows through the regenerator being multiple can mean that the second refrigerant circuit flows through the regenerator twice, or it can mean that the second refrigerant circuit flows through the regenerator three times.

[0060] In the embodiments of the present application, as an optional embodiment, please refer to Figure 2 , Figure 2 which is a schematic framework diagram of the second thermal management system provided by the embodiments of the present application. As shown in Figure 2 , the thermal management system further includes a liquid receiver / dryer, and the liquid receiver / dryer is connected to the regenerator.

[0061] This optional embodiment can store the refrigerant through the liquid receiver / dryer and separate the liquid and gas of the refrigerant entering the liquid receiver / dryer.

[0062] In the embodiments of the present application, as shown in Figure 2 , the thermal management system of the embodiments of the present application further includes a first pressure and temperature sensor PT1, a proportional valve RPV, an in-vehicle condenser ICOND, a first check valve CV1, a front compartment heat exchanger OUTCOND, a second check valve CV2, a liquid receiver / dryer 103, a regenerator IHX, a first electronic expansion valve EXV1, a battery cooler Chiller, a first electromagnetic thermal expansion valve ETXV1, an in-vehicle evaporator EVAP, a third check valve CV3, a second electromagnetic thermal expansion valve ETXV2, a vehicle-mounted refrigerator Fridge, a fourth check valve CV4, a second pressure and temperature sensor PT2, an electric multi-way valve valve, a first electric water pump pump1, a first temperature sensor T1, an electric drive system EDS, a radiator RAD, an expansion tank tank, a second temperature sensor T2, a second electric water pump pump2, a third temperature sensor T3, a power battery system BAT, and a fourth temperature sensor T4.

[0063] Specifically, the proportional valve is connected to the compressor and is also connected to the front compartment heat exchanger and the in-vehicle condenser. The proportional valve RPV is used to distribute the refrigerant flow rate ratio entering the in-vehicle condenser ICOND 1 and the front compartment heat exchanger OUTCOND. The in-vehicle condenser ICOND is used to condense the refrigerant flowing through it. During the condensation process, the heat in the refrigerant is transferred to the air in the passenger compartment, thereby achieving heating in the passenger compartment; while the front compartment heat exchanger is used for heat exchange between the outside ambient air and the refrigerant flowing inside it to achieve heat dissipation of the air conditioning system.

[0064] Further, the first check valve CV1, the second check valve CV2, the third check valve CV3, and the fourth check valve CV4 are all used to make the refrigerant flow unidirectionally only. Among them, through the first check valve, the refrigerant flowing out of the indoor condenser can flow unidirectionally into the liquid storage and dryer. Through the second check valve, the refrigerant flowing out of the regenerator can flow unidirectionally into the liquid storage and dryer. Through the third check valve, the refrigerant flowing out of the indoor evaporator can flow unidirectionally into the regenerator.

[0065] Further, the electronic expansion valve EXV1 is used to actively control the pressure reduction and expansion of the refrigerant.

[0066] Further, the battery cooler Chiller is used for heat exchange between the refrigerant and the coolant. After the two flow through the cooler, the refrigerant absorbs the heat of the coolant and the temperature rises, while the temperature of the coolant drops.

[0067] Further, the first electromagnetic thermal expansion valve ETXV1 and the second electromagnetic thermal expansion valve ETXV2 are used to control the on / off and pressure reduction and expansion of the refrigerant.

[0068] Further, the evaporator EVAP is a place where the refrigerant evaporates and absorbs heat. Through the evaporator, the air in the passenger compartment can be cooled to achieve the function of refrigerating and cooling the passenger compartment.

[0069] Further, when the refrigerant flows through the vehicle-mounted refrigerator, it can refrigerate the inside of the refrigerator;

[0070] Further, the first pressure and temperature sensor PT1 and the second pressure and temperature sensor PT2 are used to detect the temperature and pressure of the refrigerant at the corresponding positions;

[0071] Further, the electric multi-way valve valve is used to couple the coolant system. The electric drive system EDS, the radiator RAD, the power battery system BAT, the chiller chiller, etc. are connected to the channels of the electric multi-way valve to realize the coupling of the coolant system. Among them, through the switching of the mode, the electric multi-way valve valve can realize different connection methods of the above components or systems, so as to realize the most efficient energy management of the whole vehicle. The electric multi-way valve valve has multiple modes.

[0072] Specifically, as Figure 2 shown, Figure 2The first connection mode of the electric multi-way valve is shown. In this connection mode, the power battery is connected in series with the battery cooler through an electronic water valve, and the air conditioning system is in the refrigeration or refrigeration and dehumidification mode. After the high-temperature and high-pressure refrigerant at the compressor outlet dissipates heat to the environment through the outcond (external condenser), it first enters the regenerator for the first subcooling, then enters the liquid receiver for gas-liquid separation, and then enters the regenerator for the second subcooling. Passing through the regenerator twice transfers more heat to the low-temperature and low-pressure refrigerant at the compressor inlet, increasing the subcooling degree of the liquid refrigerant at the outlet of the liquid receiver and raising the superheat degree of the refrigerant at the compressor inlet, thus improving the refrigeration performance of the system. This mode can be used in the following working conditions: in medium- and high-temperature environments, the electric drive system needs to dissipate heat, the passenger compartment needs refrigeration or dehumidification, and the power battery needs to be cooled by the battery cooler.

[0073] Specifically, please refer to Figure 3 , Figure 3 which is a schematic framework diagram of the third thermal management system provided by the embodiments of the present application. As Figure 3 shown, Figure 3 The second connection mode of the electric multi-way valve is shown. In this connection mode, the electric drive system is connected in series with the battery cooler through an electronic water valve, and the air conditioning system is in the heat pump heating mode. After the high-temperature and high-pressure refrigerant at the compressor outlet dissipates heat to the passenger compartment through the Icond (internal condenser), it directly enters the liquid receiver for gas-liquid separation and then enters the regenerator for subcooling. Passing through the regenerator only once reduces the heat transferred to the low-temperature and low-pressure refrigerant at the compressor inlet, making the subcooling degree of the liquid refrigerant at the outlet of the regenerator moderate and the superheat degree of the refrigerant at the compressor inlet small. This mainly serves to ensure the dryness of the refrigerant at the compressor inlet and avoid liquid slugging of the compressor, ensuring a high energy efficiency of the heat pump heating function. This mode can be used in the following working conditions: in extremely low-temperature environments, the passenger compartment needs heating, the air conditioning system uses the heat pump mode to absorb heat from the coolant flowing through the electric drive system for heating the passenger compartment, and the power battery has no requirement or needs to be cooled (during charging).

[0074] Specifically, please refer to Figure 4 , Figure 4 which is a schematic framework diagram of the fourth thermal management system provided by the embodiments of the present application. As Figure 4 shown, Figure 4The third connection mode of the electric multi-way valve is shown. In this connection mode, the radiator is connected in series with the battery cooler through an electronic water valve, and the air-conditioning system is in the heating or heating and dehumidifying mode. After the high-temperature and high-pressure refrigerant at the compressor outlet dissipates heat to the passenger compartment through the internal condenser Icond, it directly enters the liquid storage tank for gas-liquid separation, and then enters the regenerator for subcooling. It only passes through the regenerator once, reducing the heat transferred to the low-temperature and low-pressure refrigerant at the compressor inlet, making the subcooling degree of the liquid refrigerant at the regenerator outlet moderate and the superheat degree of the refrigerant at the compressor inlet small. This mainly serves to ensure the dryness of the refrigerant at the compressor inlet and avoid liquid slugging of the compressor, ensuring high energy efficiency of the heat pump heating function. This mode can be used in the following working conditions: in medium and low temperature environments, when the passenger compartment needs heating or heating and dehumidifying, the air-conditioning system uses the heat pump mode to absorb heat from the coolant flowing through the radiator and the electric drive system to heat the passenger compartment (the coolant is heated by the air through the radiator), and the power battery has no demand.

[0075] It should be noted that the connection relationship between the coolant circuit multi-way valve and each subsystem can also be achieved by other means. In the embodiments of the present application, an electric multi-way valve is preferably used for connection, and among them, the electric multi-way valve can be an eight-way valve.

[0076] Furthermore, the first electronic water pump pump1 and the second electronic water pump pump2 are used to push the coolant to flow in the system.

[0077] Furthermore, the first temperature sensor T1, the second temperature sensor T2, the third temperature sensor T3, and the fourth temperature sensor T4 are used to detect the temperature of the coolant, so that the thermal management system controller can control the system based on the detected values.

[0078] Furthermore, the radiator RAD is a gas-liquid heat exchanger, which is used to transfer the heat of the coolant inside it to the air flowing through its surface, thereby cooling the coolant.

[0079] Furthermore, the function of the expansion tank Tank is to store and fill the coolant, accommodate the air overflowing in the system, regulate the extreme pressure of the system, etc.

[0080] In addition, please refer to Figure 5 , Figure 5 which is a schematic flowchart of a thermal management system control method provided by the embodiments of the present application. Among them, the thermal management system control method is applied to the thermal management system according to any one of the foregoing embodiments. As Figure 5 shown, the thermal management system control method of the embodiments of the present application includes the following steps:

[0081] S1. Obtain the working mode of the thermal management system;

[0082] S2. When the operating mode of the thermal management system is the heating mode, turn on the first refrigerant circuit so that the refrigerant of the thermal management system flows along the first refrigerant circuit;

[0083] S3. When the operating mode of the thermal management system is the cooling mode, turn on the second refrigerant circuit so that the refrigerant of the thermal management system flows along the second refrigerant circuit.

[0084] The method of the embodiment of the present application can obtain the operating mode of the thermal management system. Furthermore, when the operating mode of the thermal management system is the heating mode, the first refrigerant circuit can be turned on so that the refrigerant of the thermal management system flows along the first refrigerant circuit. And when the operating mode of the thermal management system is the cooling mode, the second refrigerant circuit can be turned on so that the refrigerant of the thermal management system flows along the second refrigerant circuit. Thus, in the heating mode, the heat exchange power of the regenerator can be reduced by using the first refrigerant circuit, and further the heat transferred to the low-temperature and low-pressure refrigerant at the compressor inlet can be reduced, making the subcooling degree of the liquid refrigerant at the regenerator outlet moderate and the superheat degree of the refrigerant at the compressor inlet small, mainly playing the role of ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor. On the other hand, in the cooling mode, the heat exchange power of the regenerator can be increased by using the second refrigerant circuit, and further the subcooling degree of the liquid refrigerant at the outlet of the liquid receiver dryer can be increased and the superheat degree of the refrigerant at the compressor inlet can be increased, improving the refrigeration performance of the system.

[0085] On the other hand, the embodiment of the present application provides a vehicle, which includes the thermal management system according to any one of the foregoing embodiments.

[0086] The vehicle of the embodiment of the present application can, in the heating mode, reduce the heat exchange power of the regenerator by using the first refrigerant circuit, and further reduce the heat transferred to the low-temperature and low-pressure refrigerant at the compressor inlet, making the subcooling degree of the liquid refrigerant at the regenerator outlet moderate and the superheat degree of the refrigerant at the compressor inlet small, mainly playing the role of ensuring the dryness of the refrigerant at the compressor inlet and avoiding liquid slugging of the compressor. On the other hand, in the cooling mode, the heat exchange power of the regenerator can be increased by using the second refrigerant circuit, and further the subcooling degree of the liquid refrigerant at the outlet of the liquid receiver dryer can be increased and the superheat degree of the refrigerant at the compressor inlet can be increased, improving the refrigeration performance of the system.

[0087] In the embodiments provided in this application, it should be understood that the disclosed devices and methods can be implemented in other ways. The device embodiments described above are merely illustrative. For example, the division of units is only a logical function division. In actual implementation, there may be other division methods. For another example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the displayed or discussed couplings or direct couplings or communication connections between each other can be through some communication interfaces. The indirect couplings or communication connections of devices or units can be in electrical, mechanical or other forms.

[0088] In addition, the units described as separate components may or may not be physically separated. The components displayed as units may or may not be physical units, that is, they can be located in one place or distributed to multiple network units. Some or all of the units can be selected according to actual needs to achieve the purpose of the solution of this embodiment.

[0089] Furthermore, in each embodiment of this application, the functional modules can be integrated together to form an independent part, or each module can exist alone, or two or more modules can be integrated to form an independent part.

[0090] In this document, relational terms such as first and second are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations.

[0091] The above are only the embodiments of this application and are not used to limit the protection scope of this application. For those skilled in the art, this application can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of this application shall be included in the protection scope of this application.

Claims

1. A thermal management system, characterized in that: The thermal management system comprises a regenerator and a compressor, wherein the regenerator is in communication with the compressor; The refrigerant circuit of the thermal management system comprises a first refrigerant circuit corresponding to a heating mode, and a second refrigerant circuit corresponding to a cooling mode of the thermal management system; The first refrigerant circuit is used to reduce the heat exchange power of the regenerator; The second refrigerant circuit is used to increase the heat exchange capacity of the regenerator.

2. The thermal management system according to claim 1, characterized in that: The first refrigerant circuit flows through the regenerator once.

3. The thermal management system according to claim 1, characterized in that: The second refrigerant circuit flows through the regenerator a plurality of times.

4. The thermal management system according to claim 1, characterized in that: The thermal management system further includes a liquid storage drying tank, which is in communication with the heat regenerator.

5. The thermal management system according to claim 1, characterized in that: The thermal management system also includes a proportional valve, an indoor condenser and a front cabin heat exchanger; The proportional valve is in communication with the compressor, and is in communication with the front cabin heat exchanger and the indoor condenser.

6. The thermal management system according to claim 4, characterized in that: The thermal management system further includes a first one-way valve, which is in communication with the liquid storage drying tank.

7. The thermal management system according to claim 4, characterized in that: The thermal management system further includes a second one-way valve, which is in communication with the liquid storage drying tank.

8. The thermal management system according to claim 5, characterized in that: The thermal management system further includes a third one-way valve and an indoor evaporator. The third one-way valve is in communication with the regenerator and the indoor evaporator.

9. A thermal management system control method, characterized in that: The thermal management system control method is applied to the thermal management system according to any one of claims 1 to 8, and the thermal management system control method comprises: Obtaining an operating mode for the thermal management system; When the operation mode of the thermal management system is a heating mode, opening the first refrigerant circuit so that the refrigerant of the thermal management system flows along the first refrigerant circuit; When the operation mode of the thermal management system is the cooling mode, the second refrigerant circuit is opened so that the refrigerant of the thermal management system flows along the second refrigerant circuit.

10. A vehicle, characterized in that: The vehicle comprises a thermal management system as claimed in any one of claims 1-8.

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