Thermal management system for dissipating heat from battery pack, and energy storage device

Abstract

The present application provides a thermal management system for dissipating heat from a battery pack, and an energy storage device. In the thermal management system, an output end of a compressor is in communication with a condenser and is connected to an evaporator, and is also directly connected to an input end of the evaporator by means of a bypass branch. The input end of the evaporator can selectively receive a low-temperature refrigerant from the condenser and a high-temperature gaseous refrigerant from the compressor, and the two are mixed in the evaporator, so that the low-temperature refrigerant is heated by the high-temperature gaseous refrigerant. Thus, in a low-temperature environment, the degree of superheat of a refrigerant flowing out of the evaporator can be effectively increased, preventing liquid refrigerant from being drawn into the condenser under low-temperature conditions, and eliminating the risk of drawing in air together with liquid in the condenser, thereby increasing the reliability of operation of the condenser in a low-temperature state.

Description

Heat management system for heat dissipation of battery pack and energy storage device

[0001] The present application claims priority to the Chinese patent application No. 202422193895.7, filed on September 6, 2024, and entitled "Heat management system for heat dissipation of battery pack and energy storage device", the whole content of which is incorporated herein by reference. TECHNICAL FIELD

[0002] The present application relates to the technical field of heat management, and in particular to a heat management system for heat dissipation of a battery pack and an energy storage device. BACKGROUND

[0003] In the related art heat management system, when the temperature of the application environment is relatively low, the temperature of the refrigerant flowing from the condenser to the evaporator is low, and after absorbing heat in the evaporator, the refrigerant still cannot be effectively changed into gaseous refrigerant, so that the gaseous refrigerant containing liquid refrigerant flows out from the evaporator into the compressor, resulting in poor operation stability of the compressor and low service life. SUMMARY

[0004] Embodiments of the present application provide a heat management system for heat dissipation of a battery pack and an energy storage device to improve the operation stability of the compressor when the temperature of the application environment is relatively low.

[0005] In a first aspect, the heat management system includes a compressor, at least one of a bypass branch or a condenser, at least one of a liquid-cooled evaporator or an air-cooled evaporator, and a controller. The compressor is configured to output refrigerant. The bypass branch is configured to receive the refrigerant output by the compressor. The condenser is configured to receive the refrigerant output by the compressor. The liquid-cooled evaporator is configured to receive the refrigerant output by the compressor. The air-cooled evaporator is configured to receive the refrigerant output by the compressor. The controller is configured to selectively connect at least one of an input of the bypass branch or an input of the condenser to an output of the compressor.

[0006] The liquid-cooled evaporator is configured to exchange heat between the refrigerant flowing through the liquid-cooled evaporator and a liquid-cooled plate to cool the battery pack. The air-cooled evaporator is configured to exchange heat between the refrigerant flowing through the air-cooled evaporator and air of an environment in which the battery pack is located.

[0007] In the embodiment, since the high-temperature and high-pressure gaseous refrigerant flowing out of the output end of the compressor flows out partly through the condenser and partly through the bypass branch, the refrigerant flowing out through the condenser has a low temperature and contains a large amount of liquid refrigerant, and the refrigerant flowing out through the bypass branch is still high-temperature gaseous refrigerant since it has not passed through the condenser. The output end of the compressor is selectively communicated with at least one of the input end of the condenser and the input end of the bypass branch, that is, the low-temperature refrigerant flowing out through the condenser and the high-temperature refrigerant flowing out through the bypass branch both flow to at least one of the liquid-cooled evaporator and the air-cooled evaporator, so that the refrigerant can be effectively mixed in the evaporator, the high-temperature refrigerant and the low-temperature refrigerant are fully heat-exchanged in the evaporator, the refrigerant flowing into the evaporator from the condenser is effectively heated, the superheat degree of the refrigerant at the outlet of the evaporator can be effectively improved, the suction superheat degree of the refrigerant entering the compressor is ensured, the risk of liquid suction of the compressor in a low-temperature environment can be effectively reduced or eliminated, and the operation reliability of the compressor is improved. In addition, since the thermal management system in the embodiment fully utilizes the necessary compressor of the thermal management system, only one bypass branch is added, the suction superheat degree of the compressor in a low-temperature environment can be effectively improved, the operation reliability of the compressor is improved, and the cost can be effectively saved and the competitiveness can be improved.

[0008] In some embodiments, the compressor is selectively used to deliver refrigerant to the bypass branch and the condenser respectively, and at least one of the liquid-cooled evaporator and the air-cooled evaporator is selectively used to receive refrigerant flowing out of the bypass branch and refrigerant flowing out of the condenser and is used to deliver refrigerant to the compressor. In the embodiment, the low-temperature refrigerant flowing out through the condenser and the high-temperature refrigerant flowing out through the bypass branch both flow to at least one of the liquid-cooled evaporator and the air-cooled evaporator, so that the refrigerant can be effectively mixed in at least one of the liquid-cooled evaporator and the air-cooled evaporator, the refrigerant flowing into at least one of the liquid-cooled evaporator and the air-cooled evaporator from the condenser is effectively heated, the superheat degree of the refrigerant at the outlet of at least one of the liquid-cooled evaporator and the air-cooled evaporator can be effectively improved, the suction superheat degree of the refrigerant entering the compressor is ensured, the risk of liquid suction of the compressor in a low-temperature environment can be effectively reduced or eliminated, and the operation reliability of the compressor is improved.

[0009] In some embodiments, the bypass branch includes a first throttling valve disposed on the bypass branch, the first throttling valve being configured to open or close the bypass branch, or to adjust the flow rate of the refrigerant from the output of the compressor to the input of at least one of the liquid-cooled evaporator or the air-cooled evaporator via the bypass branch. In this embodiment, the first throttling valve can control the flow rate of the refrigerant through the bypass branch, and thus can adjust the flow rate of the refrigerant through the bypass branch in different application scenarios to adjust the ratio of the low-temperature refrigerant flowing out of the condenser to the high-temperature gaseous refrigerant flowing out of the first throttling valve, thereby controlling the suction superheat of the compressor, reducing the risk of liquid suction, and improving the reliability of the compressor. The thermal management system in this embodiment can be adapted to more application scenarios.

[0010] In some embodiments, the thermal management system further includes a multi-port throttling valve, the multi-port throttling valve including a first port, a second port, and a third port;

[0011] The first port is configured to communicate with the output of the compressor;

[0012] The second port is configured to communicate with the input of the condenser, and to control the flow rate of the refrigerant from the compressor to the condenser;

[0013] The third port is configured to communicate with the input of the bypass branch, and to control the flow rate of the refrigerant from the compressor to the bypass branch.

[0014] In this embodiment, using a multi-port throttling valve instead of the first throttling valve and the second throttling valve can reduce the number of valves, thereby simplifying the control system, reducing the failure rate, and possibly reducing the overall cost.

[0015] In some embodiments, the thermal management system further includes a second throttling valve disposed on the pipeline connecting the output of the compressor and the input of the condenser, the second throttling valve being configured to control the flow rate of the refrigerant from the compressor to the condenser. In this embodiment, the flow rate of the high-temperature and high-pressure gaseous refrigerant from the output of the compressor to the condenser can be controlled by controlling the flow rate of the second throttling valve, and the ratio of the low-temperature refrigerant flowing out of the output of the condenser to the high-temperature gaseous refrigerant flowing out of the output of the bypass branch can also be controlled to ensure that the refrigerant entering the compressor has a certain suction superheat, thereby reducing the risk of liquid suction and improving the reliability of the compressor.

[0016] In some embodiments, when the temperature of the environment where the battery pack is located is less than a first threshold value or the temperature of the battery pack is less than a second threshold value, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch and the refrigerant output by the condenser and input by the compressor. That is, the compressor simultaneously receives the refrigerant transmitted by the bypass branch and the refrigerant output by the condenser. In this embodiment, when the temperature of the environment where the battery pack is located is less than the first threshold value or the temperature of the battery pack is less than the second threshold value, the bypass branch connects the output end of the compressor and the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator, so that the high-temperature gaseous refrigerant output by the compressor can be delivered to at least one of the liquid-cooled evaporator or the air-cooled evaporator through the bypass branch, mixed with the low-temperature refrigerant delivered to at least one of the liquid-cooled evaporator or the air-cooled evaporator by the condenser, and heated, thereby effectively solving the suction liquid temperature of the compressor in a low-temperature environment and improving the operation reliability of the compressor. It can be understood that when the ambient temperature is high, for example, when the temperature of the environment where the battery pack is located is greater than the first threshold value and the temperature of the battery pack is greater than the second threshold value, the bypass branch can be disconnected, and the operation stability of the compressor can be ensured.

[0017] In some embodiments, the heat management system further comprises a radiator,

[0018] When the temperature of the environment where the battery pack is located is T1, or the temperature of the battery pack is T2, the condenser is in communication with the liquid cooling plate of the battery pack for heating the battery pack, and the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch and the refrigerant output by the condenser and input by the compressor;

[0019] When the temperature of the environment where the battery pack is located is T3, and the temperature of the battery pack is T4, the radiator is in communication with the liquid cooling plate of the battery pack for heat dissipation of the battery pack;

[0020] When the temperature of the environment where the battery pack is located is T5, or the temperature of the battery pack is T6, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant output by the condenser, at least one of the liquid-cooled evaporator or the air-cooled evaporator is in communication with the liquid cooling plate of the battery pack, and at least one of the liquid-cooled evaporator or the air-cooled evaporator is used for cooling the battery pack;

[0021] Wherein, T1 < the first threshold value < T3 < T5, T2 < the second threshold value < T4 < T6.

[0022] In the embodiment, when the ambient temperature of the battery pack is T1, or the temperature of the battery pack is T2, and the temperature T1 is less than the first threshold value, and the temperature T2 is less than the second threshold value, at this temperature environment, part of the high-temperature gaseous refrigerant flowing out of the compressor flows to the condenser, and is used to exchange heat with the liquid in the liquid cooling plate of the battery pack through the condenser, thereby heating the battery pack, and the other part of the high-temperature gaseous refrigerant flowing out of the compressor flows to at least one of the liquid cooling evaporator or the air cooling evaporator through the bypass branch, and mixes and heats the refrigerant flowing from the condenser to at least one of the liquid cooling evaporator or the air cooling evaporator, so that the risk of liquid suction of the compressor suction can be effectively reduced in a low-temperature environment, and the operation stability of the compressor can be improved. When the ambient temperature of the battery pack is T3, and the temperature of the battery pack is T4, and the temperature T3 is greater than the first threshold value, and the temperature T4 is greater than the second threshold value, at this time, the ambient temperature is not low enough to cause the compressor to be unable to operate stably, so that the bypass branch is disconnected at this time, and the liquid cooling plate of the battery pack can be communicated with the heat sink at this time, and the battery pack is cooled by the heat sink, and the compressor does not need to be used to cool the battery pack, so that the energy consumption of the compressor can be effectively reduced. When the temperature is further increased, for example, when the ambient temperature of the battery pack is T5, or the temperature of the battery pack is T6, the compressor needs to work at this time, at least one of the liquid cooling evaporator or the air cooling evaporator is communicated with the liquid cooling plate of the battery pack, and is used to cool the battery pack. Since the temperature is high enough, the proportion of the liquid refrigerant in the refrigerant flowing out of at least one of the liquid cooling evaporator or the air cooling evaporator is not too high, so that part of the high-temperature refrigerant flowing out of the compressor does not need to flow to at least one of the liquid cooling evaporator or the air cooling evaporator through the bypass branch at this time.

[0023] In some embodiments, the thermal management system further comprises a sensor and a controller, the sensor is configured to detect at least one of the temperature and the pressure of the refrigerant input into the compressor, and the controller is configured to control the first throttle valve to adjust the flow of the refrigerant input from the output end of the compressor to the input end of at least one of the liquid cooling evaporator or the air cooling evaporator according to at least one of the temperature and the pressure of the refrigerant input into the compressor detected by the sensor. In the embodiment, the temperature and the pressure of the refrigerant input into the compressor can be monitored in real time by the sensor, and the suction superheat of the compressor can be monitored in real time, and then the controller controls the flow of the first throttle valve according to the information fed back by the sensor, so as to dynamically control the suction superheat of the compressor, reduce the risk of liquid suction, and improve the operation reliability of the compressor.

[0024] In some embodiments, the controller is configured to control the first throttling valve to adjust the flow rate of the refrigerant from the output end of the compressor to the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator according to at least one of the temperature and the pressure of the refrigerant input into the compressor, the temperature of the environment where the battery pack is located, or the temperature of the battery pack. In this embodiment, the flow rate of the first throttling valve can be controlled not only by monitoring at least one of the temperature or the pressure of the refrigerant input into the compressor, but also by monitoring at least one of the temperature of the environment where the battery pack is located or the temperature of the battery pack, so as to improve the fault tolerance.

[0025] In a second aspect, the embodiments of the present application provide an energy storage device, which comprises a battery pack and a thermal management system according to any one of the first aspect, and the thermal management system is configured to adjust the temperature of the battery pack or the temperature of the energy storage device. In this embodiment, the energy storage device comprises the thermal management system which has good stability in a low-temperature environment, so that the energy storage device in this embodiment can be stably operated in a low-temperature environment.

[0026] In some embodiments, when the temperature of the environment where the energy storage device is located is less than a first threshold value or the temperature of the battery pack is less than a second threshold value, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch and the refrigerant output by the condenser and input into the condenser by the compressor. That is, the compressor simultaneously receives the refrigerant transmitted by the bypass branch and the refrigerant output by the condenser. In this embodiment, when the temperature of the environment where the energy storage device is located is less than the first threshold value or the temperature of the battery pack is less than the second threshold value, the output end of the compressor is communicated with the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator through the bypass branch, so that the suction superheat of the compressor can be controlled, the risk of liquid entrainment in the suction of the compressor can be reduced, and the stability of the energy storage device can be improved.

[0027] In some embodiments, the energy storage device further comprises a power module configured to perform power conversion on the electrical energy output by the battery pack, and the second input end and the second output end of at least one of the liquid-cooled evaporator or the air-cooled evaporator are configured to be communicated with the liquid cooling plate of the power module to dissipate heat for the power module. In this embodiment, the power module can be cooled and dissipated by at least one of the liquid-cooled evaporator or the air-cooled evaporator, so that the stable operation of the power module can be ensured, and the stable operation of the energy storage device can be ensured.

[0028] In some embodiments, the energy storage device is an energy storage cabinet or a vehicle powered by the battery pack. BRIEF DESCRIPTION OF DRAWINGS

[0029] In order to more clearly illustrate the technical solutions of the embodiments of the present application or the prior art, the drawings required for use in the description of the embodiments or the prior art will be briefly introduced below.

[0030] FIG. 1 is a schematic diagram of a thermal management system according to an embodiment of the present application;

[0031] FIG. 2 is a schematic diagram of a heating battery pack mode of the thermal management system according to the embodiment of FIG. 1;

[0032] FIG. 3 is another schematic diagram of the heating battery pack mode of the thermal management system according to the embodiment of FIG. 1;

[0033] FIG. 4 is a schematic diagram of a heat pump mode of heating battery pack of the thermal management system according to the embodiment of FIG. 1;

[0034] FIG. 5 is a schematic diagram of a natural convection mode of cooling battery pack of the thermal management system according to the embodiment of FIG. 1;

[0035] FIG. 6 is a schematic diagram of a compressor refrigeration mode of cooling battery pack of the thermal management system according to the embodiment of FIG. 1;

[0036] FIG. 7 is a schematic diagram of another thermal management system according to an embodiment of the present application;

[0037] FIG. 8 is a schematic diagram of yet another thermal management system according to an embodiment of the present application;

[0038] FIG. 9 is a schematic diagram of still another thermal management system according to an embodiment of the present application;

[0039] FIG. 9A is a schematic diagram of a heating battery pack mode of the thermal management system according to the embodiment of FIG. 9;

[0040] FIG. 9B is a schematic diagram of a heat pump mode of heating battery pack of the thermal management system according to the embodiment of FIG. 9;

[0041] FIG. 9C is a schematic diagram of a natural convection mode of cooling battery pack of the thermal management system according to the embodiment of FIG. 9;

[0042] FIG. 9D is a schematic diagram of a compressor refrigeration mode of cooling battery pack of the thermal management system according to the embodiment of FIG. 9;

[0043] FIG. 10 is a schematic diagram of still another thermal management system according to an embodiment of the present application;

[0044] FIG. 10A is a schematic diagram of a heating battery pack mode of the thermal management system according to the embodiment of FIG. 10;

[0045] FIG. 10B is a schematic diagram of a heat pump mode of heating battery pack of the thermal management system according to the embodiment of FIG. 10;

[0046] FIG. 10C is a schematic diagram of a natural convection mode of cooling battery pack of the thermal management system according to the embodiment of FIG. 10;

[0047] FIG. 10D is a schematic diagram of a compressor refrigeration mode of cooling battery pack of the thermal management system according to the embodiment of FIG. 10;

[0048] FIG. 11 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0049] FIG. 12 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0050] FIG. 13 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0051] FIG. 14 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0052] FIG. 15 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0053] FIG. 15A is a schematic diagram of a heating battery pack mode of the thermal management system of the embodiment of FIG. 15;

[0054] FIG. 15B is a schematic diagram of a heating passenger cabin mode of the thermal management system of the embodiment of FIG. 15;

[0055] FIG. 15C is a schematic diagram of a heating battery pack and passenger cabin mode of the thermal management system of the embodiment of FIG. 15;

[0056] FIG. 15D is a schematic diagram of a heating battery and passenger cabin mode of the thermal management system of the embodiment of FIG. 15;

[0057] FIG. 15E is a schematic diagram of a natural cooling mode of the thermal management system of the embodiment of FIG. 15;

[0058] FIG. 15F is a schematic diagram of a compressor cooling mode of the thermal management system of the embodiment of FIG. 15;

[0059] FIG. 16 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0060] FIG. 17 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0061] FIG. 18 is a schematic diagram of another thermal management system according to embodiments of the present application;

[0062] FIG. 19 is a schematic diagram of another thermal management system according to embodiments of the present application.

[0063] Explanation of reference signs: 1, thermal management system; 10, main trunk; 11, first pipeline; 12, compressor; 13, condenser; 131, liquid-cooled condenser; 132, air-cooled condenser; 14, first expansion valve; 15, evaporator; 151, liquid-cooled evaporator; 152, air-cooled evaporator; 16, second throttle valve; 17, second expansion valve; 18, third throttle valve; 20, bypass branch; 21, second pipeline; 22, first throttle valve; 31, sensor; 32, controller; 40, heat dissipation branch; 41, third pipeline; 42, radiator; 50, heat source branch; 51, fourth pipeline; 52, battery pack; 60, first pump branch; 61, fifth pipeline; 62, first pump; 63, power module; 64, electronic control assembly; 70, second pump branch; 71, sixth pipeline; 72, second pump; 80, multi-way valve; 90, multi-way throttle valve; 91, first interface; 92, second interface; 93, third interface; 90a, three-way throttle valve; 90b, four-way throttle valve. DETAILED DESCRIPTION

[0064] The following first explains some terms related to the embodiments of the present application.

[0065] The terms "first", "second", "third", "fourth" and the like in the description and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and do not necessarily have to be used to describe a specific order or sequence. It should be understood that the data thus used can be interchanged under appropriate circumstances, so that the embodiments of the present application described herein, for example, can be implemented in an order other than those illustrated or described herein. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion, for example, a process, method, system, product or device including a series of steps or units does not have to be limited to only those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0066] The embodiments of the present application provide an energy storage device, which is an energy storage cabinet or a vehicle provided with a battery pack.

[0067] The energy storage device includes a battery pack and a thermal management system, and the thermal management system is used to adjust the temperature of the battery pack or adjust the temperature of the energy storage device. The thermal management system of the energy storage device in the embodiments has good stability in operation in a low-temperature environment. The energy storage cabinet and the vehicle are introduced respectively as follows.

[0068] The energy storage cabinet can be an industrial and commercial energy storage cabinet, a power station energy storage cabinet or a container type energy storage cabinet, etc.

[0069] For the energy storage cabinet, the energy storage cabinet includes a cabinet body and a battery pack and a thermal management system located in the cabinet body, the thermal management system is used for thermal management of the battery pack, such as refrigeration or heating of the battery pack. For some energy storage cabinets, such as industrial and commercial energy storage cabinets, etc., the thermal management system is also used for thermal management of the cabinet cavity, such as dehumidification, refrigeration or heating of the cabinet cavity, etc. Of course, for some energy storage cabinets, it also includes a power module, and the thermal management system can also be used for thermal management of the power module of the energy storage cabinet.

[0070] Specifically, the thermal management system can exchange heat with the liquid cooling plate of its battery pack to achieve thermal management of the battery pack. The power module can include a power converter and a cluster control box, etc.

[0071] However, some energy storage cabinets in the related art have poor running stability and short service life of the thermal management system when the ambient temperature is relatively low, because in the case of relatively low ambient temperature, the liquid refrigerant flowing from the condenser to the evaporator of the thermal management system cannot absorb enough heat when passing through the evaporator, resulting in that the liquid refrigerant contained in the gaseous refrigerant flowing out of the evaporator into the compressor cannot be effectively controlled, the running stability of the compressor is poor, and the service life is short.

[0072] In order to solve the problem of poor running stability of the thermal management system when the ambient temperature is relatively low, the energy storage cabinet in the embodiment provides a completely new architecture of the thermal management system, which effectively utilizes the necessary compressor in the thermal management system, effectively utilizes the high-temperature gaseous refrigerant flowing out of the compressor to supplement the heat of the refrigerant flowing from the condenser to the evaporator, so as to effectively reduce the proportion of liquid refrigerant in the refrigerant flowing out of the evaporator, effectively control the suction superheat degree of the compressor, improve the running stability and service life of the compressor, and thus effectively improve the running stability and service life of the thermal management system of the energy storage cabinet when the ambient temperature is relatively low.

[0073] For the vehicle, the vehicle includes a vehicle machine, a battery pack and a thermal management system located in the vehicle machine, the vehicle machine includes a vehicle cabin for carrying passengers or cargo, and the thermal management system is used for thermal management of its electric control assembly and vehicle-mounted battery. The thermal management system can also perform thermal management on the vehicle passenger compartment to achieve heating and refrigeration of the vehicle cabin.

[0074] The electric control assembly and the vehicle-mounted battery, etc. have their specific use temperature, such as the vehicle-mounted battery can maintain stable performance and longer power use time at 0℃-60℃. The use temperature of the electric control assembly and the vehicle-mounted assembly can be managed by the thermal management system, so that the electric control assembly and the vehicle-mounted battery can work in a suitable temperature range, thereby improving the use performance of the electric control assembly and the vehicle-mounted battery, reducing the power consumption of the vehicle, and prolonging the service life.

[0075] The vehicle-mounted battery is a battery for providing electrical energy for a vehicle, which can be a lithium ion battery, a lead-acid battery, a nickel-chromium battery, a nickel-hydrogen battery, or a sodium ion battery, etc.

[0076] The vehicle provided by the embodiments of the present application can include but is not limited to an electric vehicle / electric car, a pure electric car, a hybrid car, a range-extended electric car, a plug-in hybrid car, a new energy vehicle, etc.

[0077] Specifically, the electric control assembly and the vehicle-mounted battery can be arranged on the liquid cooling plate to realize heat dissipation, heating or heat preservation of the electric control assembly and the vehicle-mounted battery through the thermal management system.

[0078] In the related art, when the temperature of the use environment is low, such as when the vehicle is used in the winter in the cold north, the thermal management system in the vehicle has poor running stability and a short service life due to the same reason as the energy storage cabinet.

[0079] In order to solve the problem of poor running stability of the thermal management system when the environmental temperature is low, the vehicle in the embodiments provides a new architecture of the thermal management system,

[0080] The vehicle provides a new architecture of the thermal management system, which effectively utilizes the high-temperature gaseous refrigerant flowing out of the compressor to supplement the heat of the refrigerant flowing from the condenser to the evaporator, so as to effectively reduce the proportion of liquid refrigerant in the refrigerant flowing out of the evaporator, effectively control the suction superheat of the compressor, and improve the running stability and service life of the compressor, thereby effectively improving the running stability and service life of the thermal management system of the vehicle when the environmental temperature is low.

[0081] The thermal management system that can effectively improve the running stability and service life of the energy storage cabinet and the vehicle when the environmental temperature is low will be introduced in detail below.

[0082] FIG. 1 is a structural schematic diagram of a thermal management system 1 provided by the embodiments of the present application.

[0083] Referring to FIG. 1, the thermal management system 1 comprises a compressor 12, a condenser 13, an evaporator 15 and a bypass branch 20, the compressor 12, the condenser 13 and the evaporator 15 are connected in series through pipelines, and the compressor 12 is located between the output end of the evaporator 15 and the input end of the condenser 13. The compressor 12 is used to convert the refrigerant in a low-pressure gaseous state into a refrigerant in a high-pressure gaseous state; the refrigerant in a high-pressure gaseous state is liquefied after passing through the condenser 13, and the refrigerant releases heat in the condenser 13; the refrigerant becomes gaseous after absorbing heat in the evaporator 15 and is output to the compressor 12. In the thermal management system for dissipating heat for a battery pack, the condenser 13 is used to heat the battery pack 52 in the vehicle or the energy storage cabinet, and the evaporator 15 is used to cool and dissipate heat for the battery pack 52 in the vehicle or the energy storage cabinet. It can be understood that the evaporator 15 is at least one of a liquid-cooled evaporator 151 or an air-cooled evaporator 152 (as shown in FIG. 9).

[0084] The input end of the bypass branch 20 and the input end of the condenser 13 are both in communication with the output end of the compressor 12, and the output end of the bypass branch 20 and the output end of the condenser 13 are both in communication with the input end of the evaporator 15. That is, the compressor 12 is used to deliver refrigerant to the bypass branch 20 and the condenser 13, respectively, and the evaporator 15 is used to receive refrigerant flowing out of the bypass branch 20 and refrigerant flowing out of the condenser 13, and is used to deliver refrigerant to the compressor 12.

[0085] Specifically, in the thermal management system 1, the refrigerant output by the compressor 12 selectively passes through at least one of the bypass branch 20 or the condenser 13 into at least one of the liquid-cooled evaporator 151 or the air-cooled evaporator 152, the output end of the compressor 12 is used to communicate the input end of the bypass branch 20 and the input end of the condenser 13, respectively, and the output end of the bypass branch 20 and the output end of the condenser 13 are used to deliver refrigerant to the input end of at least one of the liquid-cooled evaporator 151 or the air-cooled evaporator 152, and the thermal management system 1 is used to selectively communicate at least one of the input end of the bypass branch 20 or the input end of the condenser 13 and the output end of the compressor 12.

[0086] In the embodiment, since the high-temperature and high-pressure gaseous refrigerant flowing out of the output end of the compressor 12 flows out through the condenser 13 and the bypass branch 20. The refrigerant flowing out through the condenser 13 has a lower temperature and contains a large amount of liquid refrigerant, while the refrigerant flowing out through the bypass branch 20 is still high-temperature gaseous refrigerant since it does not pass through the condenser 13. The output end of the compressor is selectively connected to at least one of the input end of the condenser and the input end of the bypass branch, that is, the low-temperature refrigerant flowing out through the condenser 13 and the high-temperature refrigerant flowing out through the bypass branch 20 both flow to the evaporator 15, so that they can be effectively mixed in the evaporator 15. The high-temperature refrigerant and the low-temperature refrigerant are fully heat-exchanged in the evaporator 15, so that the refrigerant flowing into the evaporator 15 from the condenser 13 is effectively heated, and the superheat degree of the refrigerant at the outlet of the evaporator 15 can be effectively improved to ensure that the refrigerant entering the compressor 12 has a certain suction superheat degree, thereby effectively reducing or eliminating the risk of liquid suction of the compressor 12 in a low-temperature environment and improving the operation reliability of the compressor 12. In addition, since the thermal management system 1 in the embodiment fully utilizes the existing compressor 12 of the thermal management system 1, by adding a bypass branch 20, the suction superheat degree of the compressor 12 in a low-temperature environment can be effectively improved, the operation reliability of the compressor 12 can be improved, and the cost can be effectively saved, thereby improving the competitiveness.

[0087] It can be understood that the thermal management system 1 in the embodiment can not only normally operate in a low-temperature environment, but also normally operate in a high-temperature environment. For example, in some embodiments, when the ambient temperature where the battery pack 52 is located is less than the first threshold or the temperature of the battery pack 52 is less than the second threshold, the bypass branch 20 connects the output end of the compressor 12 and the input end of the evaporator 15. At this time, the input end of the evaporator 15 receives the refrigerant transmitted by the compressor 12 through the bypass branch 20 and the refrigerant output by the condenser 13. That is, the compressor 12 simultaneously receives the refrigerant transmitted by the bypass branch 20 and the refrigerant flowing out of the condenser 13. In the embodiment, when the ambient temperature where the battery pack 52 is located is less than the first threshold or the temperature of the battery pack 52 is less than the second threshold, the bypass branch 20 connects the output end of the compressor 12 and the input end of the evaporator 15, and then the high-temperature gaseous refrigerant output by the compressor 12 can be transmitted to the evaporator 15 through the bypass branch 20 and mixed and heated with the low-temperature refrigerant transmitted to the evaporator 15 by the condenser 13, thereby effectively solving the problem of liquid suction of the compressor 12 in a low-temperature environment and improving the operation reliability of the compressor 12. It can be understood that when the ambient temperature is relatively high, for example, when the ambient temperature where the battery pack 52 is located is greater than the first threshold and the temperature of the battery pack 52 is greater than the second threshold, the bypass branch 20 can be disconnected, and the operation stability of the compressor 12 can also be ensured.

[0088] It should be noted that the ambient temperature of the battery pack 52 refers to the temperature of the accommodating cavity in which the battery pack 52 is placed, such as the atmospheric temperature of the inner cavity of the cabinet of the energy storage cabinet for placing the battery pack 52, or the atmospheric temperature of the accommodating cavity in the vehicle for placing the battery pack 52, which can be monitored in real time by a temperature sensor. The temperature of the battery pack 52 refers to the temperature collected by the temperature sensor arranged in the inner cavity of the battery pack 52.

[0089] Referring to FIG. 1, for the convenience of description, the branch in which the compressor 12, the condenser 13 and the evaporator 15 are located is set as the main branch 10, and the pipeline of the main branch 10 is set as the first pipeline 11. The main branch 10 further comprises a first expansion valve 14, which is connected between the output end of the condenser 13 and the input end of the evaporator 15.

[0090] Specifically, the compressor 12, the condenser 13, the first expansion valve 14 and the evaporator 15 are connected in series through the first pipeline 11. Among them, the compressor 12 is located between the output end of the evaporator 15 and the input end of the condenser 13, that is, the input end of the compressor 12 is communicated with the output end of the evaporator 15 through the first pipeline 11, and the output end of the compressor 12 is communicated with the input end of the condenser 13 through the first pipeline 11. The first expansion valve 14 is located between the input end of the evaporator 15 and the output end of the condenser 13, that is, the input end of the first expansion valve 14 is communicated with the output end of the condenser 13 through the first pipeline 11, and the output end of the first expansion valve 14 is communicated with the input end of the evaporator 15 through the first pipeline 11.

[0091] The main branch 10 is mainly used for the circulation of the refrigerant, wherein the first expansion valve 14 is used to form the low-temperature wet steam state refrigerant by throttling the liquid refrigerant. It should be noted that the low-temperature wet steam state refrigerant refers to the form of mist (or small droplet), at this time the refrigerant still contains part of the liquid component and has not been completely converted into gaseous refrigerant.

[0092] Specifically, the gaseous refrigerant enters the compressor 12 from the input end of the compressor 12, is processed by the compressor 12, and then high-temperature and high-pressure gaseous refrigerant is output from the output end of the compressor 12. The high-temperature and high-pressure gaseous refrigerant flows to the input end of the condenser 13 through the first pipeline 11, then enters the condenser 13 through the input end of the condenser 13, and releases heat to achieve the heating effect when passing through the condenser 13. Then the liquid refrigerant flows out through the output end of the condenser 13, and then flows to the input end of the first expansion valve 14 through the first pipeline 11. Under the action of the first expansion valve 14, the low-temperature refrigerant flows out from the output end of the first expansion valve 14, and then the low-temperature refrigerant flows to the input end of the evaporator 15 through the first pipeline 11. Then gaseous refrigerant flows out from the output end of the evaporator 15, and then flows to the input end of the compressor 12 through the first pipeline 11. Such circulation is repeated.

[0093] In this embodiment, since a part of the high-temperature and high-pressure gaseous refrigerant flowing out of the output end of the compressor 12 flows out through the condenser 13 and the first expansion valve 14 in turn, and another part flows out through the bypass branch 20. The low-temperature refrigerant flows out through the condenser 13 and the first expansion valve 14, while the refrigerant flowing out through the bypass branch 20 is still high-temperature gaseous refrigerant since it does not pass through the condenser 13. Both the low-temperature refrigerant flowing out through the condenser 13 and the first expansion valve 14 and the high-temperature refrigerant flowing out through the bypass branch 20 flow to the evaporator 15, so that they can be effectively mixed in the evaporator 15, the low-temperature refrigerant can be effectively heated, the superheat degree of the refrigerant at the outlet of the evaporator 15 can be effectively improved, and the refrigerant entering the compressor 12 has a certain suction superheat degree, so that the risk of liquid suction of the compressor 12 can be effectively reduced or eliminated in a low-temperature environment, and the operation reliability of the compressor 12 is improved. In addition, since the thermal management system 1 in this embodiment fully utilizes the existing compressor 12 of the thermal management system 1, no additional equipment for heating the low-temperature refrigerant flowing out of the first expansion valve 14 is needed, and by adding a bypass branch 20, the suction superheat degree of the compressor 12 can be effectively improved, the operation reliability of the compressor 12 can be improved, and the cost can be effectively saved and the competitiveness can be improved.

[0094] In order to effectively control the suction superheat degree of the compressor 12, in some embodiments, the flow rate of the refrigerant flowing out of the bypass branch 20 is controlled to control the suction superheat degree of the compressor 12. For example, the flow rate of the high-temperature refrigerant flowing out of the bypass branch 20 can be increased to improve the heating capacity of the low-temperature refrigerant flowing from the condenser 13 to the evaporator 15. The flow rate of the high-temperature refrigerant flowing out of the bypass branch 20 can also be reduced or closed to adjust the suction superheat degree of the compressor 12.

[0095] Referring to FIG. 1, in some embodiments, the bypass branch 20 includes a first throttling valve 22 arranged on the bypass branch 20, which is used to open or close the bypass branch 20, or to adjust the flow rate of the refrigerant input from the output end of the compressor 12 to the input end of the evaporator 15 through the bypass branch 20. For convenience of description, the pipeline of the bypass branch 20 is set as a second pipeline 21, and the first throttling valve 22 is connected in series on the second pipeline 21.

[0096] Referring to FIG. 1, in some embodiments, the input end of the first throttling valve 22 is connected between the output end of the compressor 12 and the input end of the condenser 13 through the second pipeline 21, and the output end of the first throttling valve 22 is connected between the input end of the evaporator 15 and the output end of the first expansion valve 14 through the second pipeline 21. That is, the high-temperature and high-pressure gaseous refrigerant flowing out of the output end of the compressor 12 flows part of the first pipeline 11 to the condenser 13 and the first expansion valve 14, and part of the second pipeline to the first throttling valve 22, the low-temperature refrigerant flows out of the first expansion valve 14, the high-temperature gaseous refrigerant flows out of the first throttling valve 22, then the low-temperature refrigerant flows out of the first expansion valve 14 and the high-temperature gaseous refrigerant flows out of the first throttling valve 22 are both flowed to the evaporator 15, and mixed in the evaporator 15 to heat the low-temperature refrigerant by the high-temperature gaseous refrigerant. In this embodiment, since the first throttling valve 22 can control the flow of the refrigerant through the second pipeline 21, the flow of the refrigerant through the second pipeline 21 can be adjusted and controlled by the first throttling valve 22 in different application scenarios, so as to control the ratio of the low-temperature refrigerant flowing out of the first expansion valve 14 and the high-temperature gaseous refrigerant flowing out of the first throttling valve 22, and further control the suction superheat degree of the compressor 12, reduce the risk of liquid suction, and improve the operation reliability of the compressor 12. The thermal management system 1 in this embodiment can adapt to more application scenarios.

[0097] In some embodiments, the first throttling valve 22 can be an expansion valve, which has the function of throttling and reducing pressure.

[0098] In order to realize dynamic adjustment and control of the suction superheat degree of the compressor 12 and improve the environmental adaptability of the thermal management system 1, referring to FIG. 1, in some embodiments, the thermal management system 1 further comprises a sensor 31 and a controller 32, the sensor 31 is used to detect at least one of the temperature and pressure of the refrigerant input into the compressor 12, and the controller 32 is used to control the first throttling valve 22 to adjust the flow of the refrigerant input into the input end of the evaporator 15 from the output end of the compressor 12 through the bypass branch 20 according to at least one of the temperature and pressure of the refrigerant input into the compressor 12 detected by the sensor 31. That is, after the sensor 31 detects the temperature and pressure of the refrigerant input into the compressor 12, the sensor 31 transmits the detected temperature and pressure of the refrigerant to the controller 32, and the controller 32 can receive the detection information of the sensor 31 to perform corresponding control according to the received detection information of the sensor 31.

[0099] In some embodiments, the sensor is a temperature and pressure sensor.

[0100] In this embodiment, the temperature and pressure of the refrigerant entering the compressor 12 can be monitored in real time by the sensor 31, and the suction superheat of the compressor 12 can be monitored in real time, and then the controller 32 controls the flow of the first throttling valve 22 according to the information fed back by the sensor 31, so as to dynamically control the suction superheat of the compressor 12, reduce the risk of suction liquid carrying, and improve the operation reliability of the compressor 12.

[0101] It can be understood that in other embodiments, the sensor 31 in the above can also be replaced by a humidity sensor. The humidity of the refrigerant entering the compressor 12 is detected by the humidity sensor, and the content ratio of the liquid refrigerant entering the compressor 12 is judged by the controller 32 according to the humidity of the refrigerant detected by the humidity sensor, and then the first throttling valve 22 adjusts the flow accordingly. Similarly, the risk of suction liquid carrying can be reduced, and the operation reliability of the compressor 12 can be improved.

[0102] In some embodiments, the controller 32 is configured to control the first throttling valve 22 to adjust the flow of the refrigerant from the output end of the compressor 12 to the input end of the evaporator 15 through the bypass branch 20 according to at least one of the temperature and pressure of the refrigerant entering the compressor 12 detected by the sensor 31, the ambient temperature of the battery pack 52 or the temperature of the battery pack 52. In this embodiment, not only the flow of the first throttling valve 22 can be controlled by monitoring at least one of the temperature or pressure of the refrigerant entering the compressor 12, but also the flow of the first throttling valve 22 can be controlled by monitoring at least one of the ambient temperature of the battery pack 52 or the temperature of the battery pack 52, so as to improve the fault tolerance.

[0103] Referring to FIG. 1, in some embodiments, the thermal management system 1 further comprises a second throttling valve 16. The second throttling valve 16 is arranged on a pipeline connecting the output end of the compressor 12 and the input end of the condenser 13, and the second throttling valve 16 is configured to control the flow of the refrigerant from the compressor 12 to the condenser 13.

[0104] Specifically, the second throttling valve 16 is connected in series between the output end of the compressor 12 and the input end of the condenser 13 through the first pipeline 11, and the input end of the bypass branch 20 is connected between the output end of the compressor 12 and the input end of the second throttling valve 16. In this embodiment, the flow of the second throttling valve 16 can be controlled, and then the flow of the high-temperature gaseous refrigerant from the output end of the compressor 12 to the condenser 13 can be controlled. Similarly, the proportion of the low-temperature refrigerant from the output end of the first expansion valve 14 and the high-temperature gaseous refrigerant from the output end of the bypass branch 20 can be controlled, so as to ensure that the refrigerant entering the compressor 12 has a certain suction superheat, reduce the risk of suction liquid carrying, and improve the operation reliability of the compressor 12.

[0105] In some embodiments, the second throttling valve 16 can be an expansion valve, which has the function of throttling and pressure reduction.

[0106] Referring to FIG. 1, the heat management system 1 further comprises a radiator 42, which can be understood as being generally exposed to an external environment, such as exposing the radiator 42 in an energy storage cabinet to air outside the energy storage cabinet, or exposing the radiator 42 in a vehicle to air outside the passenger compartment, to exchange heat with the external air. Through the arrangement of the radiator 42, the heat management system 1 in the embodiment can heat or cool the battery pack 52 in the energy storage cabinet or the vehicle in multiple ways. Specifically, the battery pack 52 can be heated or cooled according to the ambient temperature of the environment where the battery pack 52 is located or the temperature of the battery pack 52.

[0107] Referring to FIG. 1, for example, in some embodiments, when the ambient temperature of the environment where the battery pack 52 is located is T1, or the temperature of the battery pack 52 is T2, the condenser 13 is in communication with the liquid cooling plate of the battery pack 52 for heating the battery pack 52, and the bypass branch 20 is in communication with the output end of the compressor 12 and the input end of the evaporator 15, that is, the input end of the evaporator 15 receives the refrigerant transmitted by the compressor 12 through the bypass branch 20, and the compressor 12 inputs the refrigerant output by the condenser 13. When the ambient temperature of the environment where the battery pack 52 is located is T3, or the temperature of the battery pack 52 is T4, the radiator 42 is in communication with the liquid cooling plate of the battery pack 52 for cooling the battery pack 52; when the ambient temperature of the environment where the battery pack 52 is located is T5, or the temperature of the battery pack 52 is T6, the evaporator 15 is in communication with the liquid cooling plate of the battery pack 52 for cooling the battery pack 52, at this time the input end of the evaporator 15 receives the refrigerant output by the condenser 13, and the evaporator 15 is in communication with the liquid cooling plate of the battery pack 52, and the evaporator 15 is used to cool the battery pack 52; wherein T1 < first threshold < T3 < T5, T2 < second threshold < T4 < T6.

[0108] It can be understood that T1-T6 represents a range value, rather than a point value. In this embodiment, when the ambient temperature of the battery pack 52 is T1, or the temperature of the battery pack 52 is T2, and the temperature of T1 is less than the first threshold value, and the temperature of T2 is less than the second threshold value, at this temperature environment, part of the high-temperature gaseous refrigerant flowing out of the compressor 12 flows to the condenser 13, and is used to exchange heat with the liquid in the liquid cooling plate of the battery pack 52 through the condenser 13, and also heats the battery pack 52, and another part of the high-temperature gaseous refrigerant flowing out of the compressor 12 flows to the evaporator 15 through the bypass branch 20, and mixes and heats the refrigerant flowing from the condenser 13 to the evaporator 15, so that the suction liquid risk of the compressor 12 can be effectively reduced in a low-temperature environment, and the operation stability of the compressor 12 is improved. When the ambient temperature of the battery pack 52 is T3, and the temperature of the battery pack 52 is T4, and the temperature of T3 is greater than the first threshold value, and the temperature of T4 is greater than the second threshold value, at this time, the ambient temperature will not be low enough for the compressor 12 to operate stably, so at this time the bypass branch 20 is disconnected, for example, the flow of the first throttling valve 22 is 0, at this time the battery pack 52 can be cooled through the radiator 42 in communication with the liquid cooling plate of the battery pack 52, and the battery pack 52 is cooled without using the compressor 12 to cool the battery pack 52, which can effectively reduce the energy consumption of the compressor 12. When the temperature is further increased, for example, when the ambient temperature of the battery pack 52 is T5, or the temperature of the battery pack 52 is T6, at this time the compressor 12 needs to work, and the evaporator 15 is in communication with the liquid cooling plate of the battery pack 52, and is used to cool the battery pack 52. Since the temperature is high enough, the proportion of liquid refrigerant in the refrigerant flowing out of the evaporator 15 will not be too high, so at this time there is no need to flow part of the high-temperature refrigerant flowing out of the compressor 12 to the evaporator 15 through the bypass branch 20.

[0109] Referring to FIG. 1, in some embodiments, the condenser 13 comprises a liquid-cooled condenser 131 for heat exchange between the refrigerant flowing through the liquid-cooled condenser 131 and other liquid flowing through the liquid-cooled condenser 131, the liquid-cooled condenser 131 comprises a first input end and a first output end in communication and a second input end and a second output end in communication, it can be understood that the first input end and the first output end of the liquid-cooled condenser 131 correspond to the inlet and outlet of the refrigerant side of the liquid-cooled condenser 131, and the second input end and the second output end of the liquid-cooled condenser 131 correspond to the inlet and outlet of the water-cooled side of the liquid-cooled condenser 131. The evaporator 15 comprises a liquid-cooled evaporator 151 for heat exchange between the refrigerant flowing through the liquid-cooled evaporator 151 and other liquid flowing through the liquid-cooled evaporator 151, the liquid-cooled evaporator 151 comprises a first input end and a first output end in communication and a second input end and a second output end in communication; it can be understood that the first input end and the first output end of the liquid-cooled evaporator 151 correspond to the inlet and outlet of the refrigerant side of the liquid-cooled evaporator 151, and the second input end and the second output end of the liquid-cooled evaporator 151 correspond to the inlet and outlet of the water-cooled side of the liquid-cooled evaporator 151. The input end of the bypass branch 20 and the first input end of the condenser 13 are both in communication with the output end of the compressor 12, and the output end of the bypass branch 20 and the first output end of the condenser 13 are both in communication with the first input end of the evaporator 15.

[0110] It can be understood that the heating and cooling of the battery pack 52 by the thermal management system 1 can be autonomously controlled, in order to effectively control the heating or cooling of the battery pack 52 by the thermal management system 1, referring to FIG. 1, the thermal management system 1 further comprises a multi-way valve 80 and a controller 32, the multi-way valve 80 comprises an interface for communicating the liquid-cooled plate of the battery pack 52, an interface for communicating the radiator 42, an interface for communicating the second input end and the second output end of the condenser 13, and an interface for communicating the second input end and the second output end of the evaporator 15; the controller 32 is used to control the communication mode between the interfaces of the multi-way valve 80.

[0111] For example, in some embodiments, when the ambient temperature where the battery pack 52 is located is T1, or the temperature of the battery pack 52 is T2, the controller 32 controls the multi-way valve 80 to communicate with the interface of the condenser 13 and the interface of the battery pack 52 with the liquid cooling plate, and the bypass branch 20 communicates the output end of the compressor 12 and the input end of the evaporator 15, for example, by controlling the flow of the first throttle valve 22 to be greater than 0. When the ambient temperature where the battery pack 52 is located is T3, or the temperature of the battery pack 52 is T4, the controller 32 controls the multi-way valve 80 to communicate with the radiator 42 and the interface of the battery pack 52 with the liquid cooling plate; when the ambient temperature where the battery pack 52 is located is T5, or the temperature of the battery pack 52 is T6, the controller 32 controls the multi-way valve 80 to communicate with the evaporator 15 and the interface of the battery pack 52 with the liquid cooling plate. In this embodiment, through the control of the controller 32 on the multi-way valve 80, and the control of the controller 32 on the multi-way valve 80, the heating or cooling mode of the thermal management system 1 to the battery pack 52 can be adjusted in real time according to the real-time monitored temperature, so that the battery pack 52 is always at a suitable working temperature to improve the performance of the battery pack 52.

[0112] It can be understood that, in order to improve the heat exchange efficiency of the liquid of the liquid cooling plate of the battery pack 52 with the condenser 13 or the evaporator 15, the thermal management system 1 further comprises a first pump 62 and a second pump 72, which are used to accelerate the flow rate of the liquid flowing through the liquid cooling plate of the battery pack 52 in different modes. The first pump 62 and the second pump 72 are respectively communicated with the interfaces of the multi-way valve 80, so as to control the first pump 62 or the second pump 72 to communicate with the liquid cooling plate of the battery pack 52 through the control valve.

[0113] Referring to FIG. 1, for the convenience of description, the branch where the radiator 42 is located is set as a heat dissipation branch 40, the pipeline of the heat dissipation branch 40 is a third pipeline 41, and the radiator 42 is arranged on the third pipeline 41. The branch where the battery pack 52 is located is set as a heat source branch 50, the pipeline of the heat source branch 50 is a fourth pipeline 51, and the battery pack 52 is a heat source connected in series on the fourth pipeline 51. The branch where the first pump 62 is located is a first pump branch 60, the pipeline of the first pump branch 60 is a fifth pipeline 61, and the first pump 62 is connected in series on the fifth pipeline 61. The branch where the second pump 72 is located is a second pump branch 70, the pipeline of the second pump branch 70 is a sixth pipeline 71, and the second pump 72 is connected in series on the sixth pipeline 71.

[0114] The heat dissipation branch 40, the heat source branch 50, the first pump branch 60 and the second pump branch 70 are all connected to the multi-way valve 80, so as to realize the conversion of the mode of the thermal management system 1 through the multi-way valve 80.

[0115] It can be understood that the number of the multi-way valve 80 can be one or multiple. For example, in some embodiments, the multi-way valve 80 includes a first interface, a second interface, a third interface, a fourth interface, a fifth interface, a sixth interface, a seventh interface, and an eighth interface. The heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 are connected to the first interface, the second interface, the third interface, the fourth interface, the fifth interface, the sixth interface, the seventh interface, and the eighth interface of the multi-way valve 80, respectively, to realize integrated linkage of the heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 through the multi-way valve 80.

[0116] It should be noted that each interface of the multi-way valve 80 in the drawings is marked with a number. The first interface corresponds to the number 1 in the drawings, the second interface corresponds to the number 2 in the drawings, the third interface corresponds to the number 3 in the drawings, the fourth interface corresponds to the number 4 in the drawings, the fifth interface corresponds to the number 5 in the drawings, the sixth interface corresponds to the number 6 in the drawings, the seventh interface corresponds to the number 7 in the drawings, and the eighth interface corresponds to the number 8 in the drawings.

[0117] Specifically, referring to FIG. 1, the input end and the output end of the heat dissipation branch 40 are in communication with two interfaces of the multi-way valve 80. For example, the input end of the radiator 42 can be in communication with the fourth interface through the third pipeline 41, and the output end of the radiator 42 can be in communication with the first interface through the third pipeline 41.

[0118] The input end and the output end of the heat source branch 50 are in communication with another two interfaces of the multi-way valve 80. For example, the input end of the battery pack 52 can be in communication with the second interface through the fourth pipeline 51, and the output end of the battery pack 52 can be in communication with the seventh interface through the fourth pipeline 51. It can be understood that the battery pack 52 is in communication with the second interface and the fourth interface of the multi-way valve 80 through the fourth pipeline 51 via its liquid cooling plate.

[0119] The first input end of the liquid-cooled condenser 131 is in communication with the output end of the compressor 12 through the first pipeline 11, and the first output end of the liquid-cooled condenser 131 is in communication with the first expansion valve 14 through the first pipeline 11. It should be noted that the liquid-cooled condenser 131 is a liquid-liquid heat exchange, such as a refrigerant-water heat exchange.

[0120] The fifth pipeline 61 respectively communicates with the second input end and the second output end of the liquid-cooled condenser 131, so as to connect the condenser 13 and the first pump 62 in series, and the input end and the output end of the first pump branch 60 communicate with the other two interfaces of the multi-way valve 80. For example, the output end of the first pump 62 can be connected to the second input end of the liquid-cooled condenser 131 through the fifth pipeline 61, the input end of the first pump 62 can be connected to the sixth interface through the fifth pipeline 61, and the second output end of the liquid-cooled condenser 131 can be connected to the fifth interface through the fifth pipeline 61. It can be understood that the first pump 62 can be a water pump.

[0121] The first input end of the liquid-cooled evaporator 151 is connected to the output end of the first expansion valve 14 through the first pipeline 11, and the first output end of the liquid-cooled evaporator 151 is connected to the input end of the compressor 12 through the first pipeline 11. It should be noted that the liquid-cooled evaporator 151 is a liquid-liquid heat exchange, such as a refrigerant-water heat exchange.

[0122] The sixth pipeline 71 respectively communicates with the second input end and the second output end of the liquid-cooled evaporator 151, and connects the first pump 62 and the evaporator 15 in series, and the input end and the output end of the second pump branch 70 communicate with the other two interfaces of the multi-way valve 80. For example, the output end of the second pump 72 can be connected to the second input end of the liquid-cooled evaporator 151 through the sixth pipeline 71, the input end of the second pump 72 can be connected to the eighth interface through the sixth pipeline 71, and the second output end of the liquid-cooled evaporator 151 can be connected to the third interface. It can be understood that the second pump 72 can be a water pump.

[0123] By changing the connection mode of the eight interfaces of the multi-way valve 80, the heat management system 1 in the embodiment can be transformed into different modes to cope with different working scenarios.

[0124] FIG. 2 is one of the schematic diagrams of the heating battery pack 52 mode of the heat management system 1 in the embodiment of FIG. 1.

[0125] Referring to FIG. 2, the heat management system 1 includes a heating battery pack 52 mode, which is mainly applied to a scenario with a relatively low ambient temperature, such as when the ambient temperature where the battery pack 52 is located is less than a first threshold value or the temperature of the battery pack 52 is less than a second threshold value. In this mode, the bypass branch connects the output end of the compressor 12 and the input end of the liquid-cooled evaporator 151, and the liquid-cooled condenser 131 communicates with the liquid-cooled plate of the battery pack 52 to heat the battery pack 52.

[0126] Specifically, the first interface and the eighth interface of the multi-way valve 80 are connected, the second interface and the fifth interface are connected, the third interface and the fourth interface are connected, and the sixth interface and the seventh interface are connected.

[0127] At this time, the heat source branch 50 and the first pump branch 60 are connected through the multi-way valve 80, and the liquid (such as water) from the output end of the battery pack 52 flows through the seventh interface, the sixth interface to the input end of the first pump 62, then flows from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and flows from the second output end of the liquid-cooled condenser 131 to the fifth interface, the second interface, and finally to the input end of the battery pack 52, and so on. During the circulation process, the high-temperature gaseous refrigerant from the output end of the compressor 12 to the liquid-cooled condenser 131 exchanges heat with the liquid from the first water pump to the liquid-cooled condenser 131, so that the temperature of the liquid flowing to the battery pack 52 is increased, and the battery pack 52 can be heated.

[0128] At the same time, the second pump branch 70 and the heat dissipation branch 40 are connected through the multi-way valve 80, specifically, the first interface and the eighth interface are connected, and the third interface and the fourth interface are connected, and the liquid (such as water) from the radiator 42 flows through the first interface, the eighth interface to the second pump 72, then flows from the second pump 72 to the second input end of the liquid-cooled evaporator 151, and flows from the second output end of the liquid-cooled evaporator 151 to the third interface, the fourth interface, and finally to the radiator 42, and so on. During the circulation process of the liquid, when passing through the liquid-cooled evaporator 151, it exchanges heat with the low-temperature refrigerant in the liquid-cooled evaporator 151, and the liquid flowing from the liquid-cooled evaporator 151 to the radiator 42 is cooled, and the cooled liquid flows through the radiator 42 and exchanges heat with the external air. In this process, the heat of the external air is used to heat the low-temperature refrigerant to make the refrigerant gaseous.

[0129] In this mode, the high-temperature and high-pressure gaseous refrigerant from the output end of the compressor 12, part of which is used to heat and cool the battery pack 52 through the liquid-cooled condenser 131, and then forms low-temperature refrigerant through the first expansion valve 14, and the other part flows to the liquid-cooled evaporator 151 in the form of high-temperature gaseous refrigerant through the first throttle valve 22, and mixes with the low-temperature refrigerant in the liquid-cooled evaporator 151 to heat the low-temperature refrigerant. The low-temperature refrigerant in this mode not only absorbs heat from the external environment when passing through the liquid-cooled evaporator 151, but also can be heated by the high-temperature gaseous refrigerant flowing from the bypass branch 20, so that it can be fully heated to become gaseous refrigerant even in the case of low ambient temperature, so as to control the suction superheat degree of the compressor 12 within the normal range, reduce the risk of liquid suction of the compressor 12, and improve the operation reliability of the compressor 12.

[0130] Fig. 3 is another schematic diagram of the heating mode of the battery pack 52 of the heat management system 1 in the embodiment of Fig. 1.

[0131] Referring to FIG. 3, the main difference between the heating battery pack 52 mode in the embodiment of FIG. 3 and that of FIG. 2 is that the third interface and the eighth interface are in communication, the first interface and the fourth interface are in communication, and the liquid cooling evaporator 151 in this embodiment is no longer in communication with the heat sink 42, i.e., the refrigerant flowing through the liquid cooling evaporator 151 can no longer absorb heat from the external air. At this time, the high-temperature and high-pressure gaseous refrigerant flowing out of the output end of the compressor 12, part of which passes through the liquid cooling condenser 131 to heat and cool the battery pack 52, and then forms low-temperature refrigerant through the first expansion valve 14, and the other part directly flows to the liquid cooling evaporator 151 in the form of high-temperature gaseous refrigerant, and mixes with the low-temperature refrigerant in the liquid cooling evaporator 151 to heat the low-temperature refrigerant.

[0132] In this embodiment, the low-temperature refrigerant flowing out of the first expansion valve 14 can no longer absorb heat from the external air, and most of the heat comes from the high-temperature gaseous refrigerant flowing out of the bypass branch 20. The heating mode in this embodiment can be applied in an extremely low temperature environment, such as an application scenario where the ambient temperature is lower than the boiling point of the refrigerant.

[0133] FIG. 4 is a schematic diagram of the heat pump mode of the heat management system 1 in the embodiment of FIG. 1 for heating the battery pack 52.

[0134] Referring to FIG. 4, in some embodiments, the heat management system 1 further includes an air source heat pump mode for heating the battery pack 52. The heat pump mode in this embodiment is mainly applied when the ambient temperature of the environment where the battery pack 52 is located is greater than a first threshold value and the temperature of the battery pack 52 is greater than a second threshold value, at which time the bypass branch 20 is disconnected, the output end of the compressor 12 and the input end of the liquid cooling evaporator 151 are not in communication, and the liquid cooling condenser 131 is in communication with the liquid cooling plate of the battery pack 52 to heat the battery pack 52. The main difference between this embodiment and the embodiment of FIG. 2 is that the hot gas bypass branch 20 is disconnected, i.e., the second pipeline 21 is disconnected by the first throttle valve 22, the high-temperature and high-pressure gaseous refrigerant flowing out of the output end of the compressor 12 all flows to the liquid cooling condenser 131, then flows to the liquid cooling evaporator 151 through the first expansion valve 14, and exchanges heat with the liquid (such as water) flowing through the liquid cooling evaporator 151, and the heat of the liquid flowing through the liquid cooling evaporator 151 is absorbed from the air in the external environment through the heat sink 42, i.e., most of the heat absorbed by the low-temperature refrigerant flowing out of the first expansion valve 14 when passing through the liquid cooling evaporator 151 comes from the air in the external environment.

[0135] The heat pump mode in this embodiment is applied in an environment with a higher temperature than that in the embodiment of FIG. 2.

[0136] FIG. 5 is a schematic diagram of the natural cooling mode of the heat management system 1 in the embodiment of FIG. 1 for cooling the battery pack 52.

[0137] Referring to FIG. 5, in some embodiments, the thermal management system 1 comprises a natural cooling mode for cooling the battery pack 52. The natural cooling mode in the present embodiment is mainly applied in the case that the ambient temperature of the environment where the battery pack 52 is located and the temperature of the battery pack 52 are both higher than the temperatures in the embodiment of FIG. 4, i.e. the case that the battery pack needs to be cooled. In this mode, the bypass branch 20 is disconnected, the output end of the compressor 12 is not connected to the input end of the liquid-cooled evaporator 151, and the radiator 42 is connected to the liquid-cooled plate of the battery pack 52 for cooling the battery pack 52.

[0138] Specifically, in the natural cooling mode, the first interface and the eighth interface of the multi-way valve 80 are connected, the second interface and the third interface are connected, the fourth interface and the fifth interface are connected, and the sixth interface and the seventh interface are connected. In this mode, the first throttle valve 22 and the second throttle valve 16 are disconnected, and the compressor 12 does not work.

[0139] In this mode, the heat source branch 50, the first pump branch 60, the second pump branch 70 and the heat dissipation branch 40 are connected in series through the multi-way valve 80, respectively. The liquid (such as water) flowing out of the output end of the battery pack 52 flows through the seventh interface and the sixth interface to the input end of the first pump 62, then flows from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and then flows from the second output end of the liquid-cooled condenser 131 to the fifth interface and the fourth interface, and then flows to the output end of the radiator 42, and then flows out through the output end of the radiator 42, and then flows through the first interface and the eighth interface to the input end of the second pump 72, and then flows from the output end of the second pump 72 to the second input end of the liquid-cooled evaporator 151, and then flows from the second output end of the liquid-cooled evaporator 151 to the third interface and the second interface, and finally flows to the input end of the battery pack 52, and then circulates in this way. In this mode, the liquid flowing through the battery pack 52 exchanges heat with the heat generated by the battery pack 52, and the temperature of the liquid flowing out of the battery pack 52 is increased, and then exchanges heat with the air in the external environment when flowing through the radiator 42, so that the temperature of the liquid flowing through the radiator 42 is reduced, thereby cooling the battery pack 52. Since the first throttle valve 22 and the second throttle valve 16 are disconnected, the compressor 12 does not work, so that the cooling of the battery pack 52 in this mode can be achieved by the natural cooling of the radiator 42. Since the compressor 12 does not work, the energy consumption can be effectively reduced.

[0140] It can be understood that the temperature of the environment where the natural cooling mode in the present embodiment is applied is generally higher than the temperature of the environment where the heat pump mode in the embodiment of FIG. 4 is applied.

[0141] FIG. 6 is a schematic diagram of the compressor 12 cooling mode of the thermal management system 1 in the embodiment of FIG. 1 for cooling the battery pack 52.

[0142] Referring to FIG. 6, in some embodiments, the thermal management system 1 includes a compressor 12 refrigeration mode for cooling the battery pack 52. The compressor 12 refrigeration mode in the present embodiment is mainly applied to the case where both the ambient temperature of the environment where the battery pack 52 is located and the temperature of the battery pack 52 are higher than those in the embodiment of FIG. 5, and the battery pack also needs to be cooled. In this mode, the bypass branch 20 is disconnected, and the output end of the compressor 12 is not communicated with the input end of the liquid-cooled evaporator 151. The liquid-cooled evaporator 151 is communicated with the liquid-cooled plate of the battery pack 52 for refrigeration and heat dissipation of the battery pack 52.

[0143] Specifically, in the compressor 12 refrigeration mode, the first interface and the sixth interface of the multi-way valve 80 are communicated, the second interface and the third interface are communicated, the fourth interface and the fifth interface are communicated, and the seventh interface and the eighth interface are communicated. In addition, in this mode, the first throttling valve 22 is disconnected to disconnect the bypass branch 20.

[0144] In this mode, the compressor 12 works normally, the liquid-cooled evaporator 151 can achieve refrigeration, and the liquid-cooled condenser 131 can achieve heating.

[0145] The heat source branch 50 and the second pump branch 70 are communicated through the multi-way valve 80. The liquid (such as water) flowing out of the output end of the battery pack 52 flows through the seventh interface and the eighth interface to the input end of the second pump 72, then flows out of the output end of the second pump 72 to the second input end of the liquid-cooled evaporator 151, and then flows through the second output end of the liquid-cooled condenser 131 to the third interface, the second interface, and finally to the input end of the battery pack 52, and so on. In the circulation process, the low-temperature refrigerant flowing out of the output end of the first expansion valve 14 and the liquid flowing out of the second water pump to the liquid-cooled evaporator 151 exchange heat, so that the temperature of the liquid flowing out of the liquid-cooled evaporator 151 is reduced, and the low-temperature liquid can cool the battery pack 52 when flowing through the battery pack 52.

[0146] At the same time, the heat dissipation branch 40 and the first pump branch 60 are communicated through the multi-way valve 80. The liquid (such as water) output from the heat sink 42 flows through the first interface and the sixth interface to the first pump 62, then flows through the first pump 62 to the second input end of the liquid-cooled condenser 131, and then flows through the second output end of the liquid-cooled condenser 131 to the fifth interface, the fourth interface, and finally to the heat sink 42, and so on. In the circulation process of the liquid, the liquid exchanges heat with the high-temperature gaseous refrigerant in the liquid-cooled condenser 131 when passing through the liquid-cooled condenser 131, and the temperature of the liquid flowing out of the liquid-cooled condenser 131 to the heat sink 42 is increased. The liquid with increased temperature can exchange heat with the external air when flowing through the heat sink 42, and the heat is dissipated to the external air. Such circulation can achieve refrigeration of the battery pack 52.

[0147] It can be understood that the temperature of the environment in which the compressor 12 in the present embodiment is applied in the refrigeration mode is generally high, and is generally higher than the temperature of the environment in which the natural heat dissipation mode in the embodiment of FIG. 5 is applied.

[0148] FIG. 7 is a schematic diagram of another heat management system 1 provided by the present application.

[0149] Referring to FIG. 7, the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 can refer to the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 in the embodiment of FIG. 1, and will not be described here again. The main difference between the heat management system 1 in the present embodiment and the heat management system 1 in the embodiment of FIG. 1 is that the main trunk 10 in the present embodiment is not provided with the second throttle valve 16, and the other structures of the main trunk 10 are the same. In the present embodiment, since the second throttle valve 16 is not provided, the proportion of the refrigerant flowing out of the output end of the compressor 12 to the condenser 13 and the bypass branch 20 can be adjusted by the first throttle valve 22, so as to effectively control the suction superheat degree of the compressor 12.

[0150] It can be understood that the heat management system 1 in the present embodiment also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5), and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the working modes are basically the same as those of the heat management system 1 in the embodiment of FIG. 1, and will not be described here again.

[0151] FIG. 8 is a schematic diagram of another heat management system 1 provided by the present application.

[0152] Referring to FIG. 8, the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 can refer to the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 in the embodiment of FIG. 1, and will not be described here again. The main difference between the heat management system 1 in the present embodiment and the heat management system 1 in the embodiment of FIG. 1 is that a multi-pass throttle valve 90 is used to replace the first throttle valve 22 and the second throttle valve 16 in the embodiment of FIG. 1 in the present embodiment.

[0153] Specifically, the heat management system 1 further comprises a multi-port throttling valve 90, such as a three-port throttling valve 90a, the multi-port throttling valve 90 comprising a first port 91, a second port 92 and a third port 93, the first port 91 being in communication with the output of the compressor 12 via the first pipeline 11, the second port 92 being in communication with the input of the condenser 13 via the first pipeline 11, and the third port 93 being in communication with the input of the bypass branch 20. In this embodiment, the use of the three-port throttling valve 90a instead of the first throttling valve 22 and the second throttling valve 16 can reduce the number of valves, thereby simplifying the control system, reducing the failure rate, and possibly reducing the overall cost.

[0154] It can be understood that the multi-port throttling valve 90 in this embodiment has the function of throttling, and can control the flow through the first port 91, the second port 92 and the third port 93. In some embodiments, the multi-port throttling valve 90 can be a multi-port expansion valve, which has the function of throttling and pressure reduction.

[0155] FIG. 9 is a schematic diagram of another heat management system 1 according to an embodiment of the present application.

[0156] Referring to FIG. 9, the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60 and the second pump branch 70 can refer to the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60 and the second pump branch 70 in the embodiment of FIG. 1, and will not be described here again. The main difference between the heat management system 1 of this embodiment and the heat management system 1 of the embodiment of FIG. 1 is the structure of the main pipeline 10.

[0157] Referring to FIG. 9, in some embodiments, the number of evaporators 15 is multiple, and the multiple evaporators 15 comprise an air-cooled evaporator 152 and a liquid-cooled evaporator 151. The air-cooled evaporator 152 is used for heat exchange between the refrigerant flowing through the air-cooled evaporator 152 and the gas outside the air-cooled evaporator 152, such as being used for refrigeration and heat dissipation for the inner cavity of the energy storage cabinet, or being used for refrigeration for the vehicle passenger compartment. The liquid-cooled evaporator 151 is used for heat exchange between the refrigerant flowing through the liquid-cooled evaporator 151 and other liquids flowing through the liquid-cooled evaporator 151, such as being used for refrigeration and heat dissipation for the battery pack 52 in the energy storage cabinet or the battery pack 52 of the vehicle. In this embodiment, the outputs of the bypass branch 20 are in communication with the input of the air-cooled evaporator 152 and the output of the first expansion valve 14, respectively.

[0158] Referring to FIG. 9, in some embodiments, the heat management system 1 further comprises a second expansion valve 17 connected to the first input end of the liquid-cooled evaporator 151 and the output end of the condenser on the pipeline, and the branch in which the air-cooled evaporator 152 and the first expansion valve 14 are located is connected in parallel with the branch in which the liquid-cooled evaporator 151 and the second expansion valve 17 are located, at this time, the first input end of the liquid-cooled evaporator 151 is connected to the output end of the second expansion valve 17 through the first pipeline 11, the first output end of the liquid-cooled evaporator 151 is connected to the input end of the compressor 12 through the first pipeline 11, and the input end of the second expansion valve 17 is connected to the output end of the condenser 13 through the first pipeline 11. That is, the refrigerant flowing out of the condenser 13 can flow to the compressor 12 through the first expansion valve 14 and the air-cooled evaporator 152 in turn, can flow to the compressor 12 through the second expansion valve 17 and the liquid-cooled evaporator 151 in turn, or can be divided into two parts and flow to the first expansion valve 14 and the second expansion valve 17, respectively. In this embodiment, since the main pipeline 10 comprises the liquid-cooled evaporator 151 and the air-cooled evaporator 152, not only the battery pack 52 of the heat source branch 50 can be cooled by the liquid-cooled evaporator 151, but also the inner cavity of the energy storage cabinet or the vehicle passenger compartment can be cooled by the air-cooled evaporator 152, thereby improving the functional diversity of the heat management system 1 in this embodiment.

[0159] The second pump branch 70 is connected to the liquid-cooled evaporator 151, and the connection mode is the same as that in the embodiment of FIG. 1, which will not be described here.

[0160] Referring to FIG. 9, in some embodiments, the fifth pipeline 61 is connected to the second input end and the outlet of the liquid-cooled condenser 131, respectively, and the liquid-cooled condenser 131, the first pump 62 and the power module 63 are connected in series.

[0161] Referring to FIG. 9, in some embodiments, the first pump branch 60 further comprises a power module 63 connected in series to the fifth pipeline 61, and the power module 63 is connected in series between the first pump 62 and the liquid-cooled condenser 131, that is, the liquid flowing out of the first pump 62 flows through the power module 63 and then flows through the liquid-cooled condenser 131. Since the power module 63 is connected in series between the first pump 62 and the liquid-cooled condenser 131, the heat source branch 50 and the first pump branch 60 are connected, and when the battery pack 52 of the heat source branch 50 is heated by the liquid-cooled condenser 131, the liquid flowing to the power module 63 is the liquid cooled by the battery pack 52, thereby reducing the heating effect of the liquid-cooled condenser 131 on the power module 63. This embodiment is mainly applied to the scene where the battery pack 52 needs to be heated, but the power module 63 does not need to be heated.

[0162] It can be understood that the heat management system 1 in the embodiment of FIG. 9 also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5), and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the modes are basically the same as those of the heat management system 1 in the embodiment of FIG. 1.

[0163] FIG. 9A is a schematic diagram of the mode of heating the battery pack 52 of the heat management system 1 in the embodiment of FIG. 9.

[0164] Referring to FIG. 9A, the compressor 12 refrigeration mode in the embodiment is mainly applied to a scenario where the ambient temperature is low, such as when the ambient temperature where the battery pack 52 is located is less than a first threshold value or the temperature of the battery pack 52 is less than a second threshold value. In this mode, the bypass branch 20 is connected between the output end of the compressor 12 and the input end of the air-cooled evaporator 152, and the liquid-cooled condenser 131 is connected to the liquid-cooled plate of the battery pack 52 to heat the battery pack 52.

[0165] Specifically, in the mode of heating the battery pack 52 in the embodiment, the second interface and the fifth interface are connected, and the sixth interface and the seventh interface are connected, so as to connect the first pump branch 60 and the heat source branch 50 through the multi-way valve 80. The second expansion valve 17 and the branch where the liquid-cooled evaporator 151 is located are disconnected, that is, the second expansion valve 17 is disconnected, and the refrigerant flowing out of the condenser 13 will not flow through the second expansion valve 17 and the liquid-cooled evaporator 151, and the bypass branch 20 is not connected to the branch where the second expansion valve 17 and the liquid-cooled evaporator 151 are located. Therefore, the air-cooled evaporator 152 cannot absorb heat from the external environment through the radiator 42 in the mode of heating the battery pack 52, so that in the embodiment, the connection mode between the first interface, the fourth interface, the third interface, and the eighth interface can be consistent with that of the embodiment of FIG. 2 or consistent with that of the embodiment of FIG. 3.

[0166] Taking the application of the mode of heating the battery pack 52 in the embodiment in the energy storage cabinet as an example, not only can the battery pack 52 be heated as in the embodiments of FIG. 2 or FIG. 3, but also the air-cooled evaporator 152 can absorb heat from the inner cavity of the energy storage cabinet to cool and dehumidify the inner cavity of the energy storage cabinet.

[0167] FIG. 9B is a schematic diagram of the heat pump mode of heating the battery pack 52 of the heat management system 1 in the embodiment of FIG. 9.

[0168] Referring to FIG. 9B, the heat pump mode in the present embodiment is mainly applied when the ambient temperature where the battery pack 52 is located is greater than the first threshold value and the temperature of the battery pack 52 is greater than the second threshold value, at this time, the bypass branch 20 is disconnected, the output end of the compressor 12 and the input end of the air-cooled evaporator 152 are not communicated, the liquid-cooled condenser 131 is communicated with the liquid-cooled plate of the battery pack 52 to heat the battery pack 52. In the heat pump mode in the present embodiment, the first throttle valve 22 needs to be disconnected as in the embodiment of FIG. 4 to disconnect the bypass branch 20. The first expansion valve 14 can also be disconnected to disconnect the branch where the first expansion valve 14 and the air-cooled evaporator 152 are located. The working principle of the heat pump mode in the present embodiment and the connection mode with the multi-way valve 80 are basically the same as in the embodiment of FIG. 4. Please refer to the embodiment of FIG. 4, which will not be repeated here.

[0169] It can be understood that in the heat pump mode in the present embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened at the same time to make the branch where the first expansion valve 14 and the air-cooled evaporator 152 are located also communicated.

[0170] FIG. 9C is a schematic diagram of the natural cooling mode of the heat management system 1 in the embodiment of FIG. 9 cooling the battery pack 52.

[0171] Referring to FIG. 9C, the natural cooling mode in the present embodiment is mainly applied when the ambient temperature where the battery pack 52 is located and the temperature of the battery pack 52 are both higher than in the embodiment of FIG. 9B, that is, the battery pack 52 needs to be cooled. In this mode, the bypass branch 20 is disconnected, the output end of the compressor 12 and the input end of the air-cooled evaporator 152 are not communicated, and the radiator 42 is communicated with the liquid-cooled plate of the battery pack 52 to cool the battery pack 52. In the natural cooling mode in the present embodiment, the first expansion valve 14, the second expansion valve 17, the first throttle valve 22 and the second throttle valve 16 need to be disconnected at the same time, and the compressor 12 does not work. As for the working principle of the natural cooling mode in the present embodiment and the connection mode with the multi-way valve 80, they are basically the same as in the embodiment of FIG. 5. Please refer to the embodiment of FIG. 5, which will not be repeated here.

[0172] FIG. 9D is a schematic diagram of the compressor 12 refrigeration mode of the heat management system 1 in the embodiment of FIG. 9 cooling the battery pack 52.

[0173] Referring to FIG. 9D, the compressor 12 refrigeration mode in the embodiment is mainly applied to the case where the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are both higher than those in the embodiment of FIG. 9C, and the battery pack 52 also needs to be cooled. In this mode, the bypass branch 20 is disconnected, the output end of the compressor 12 is not communicated with the input end of the air-cooled evaporator 152, and the liquid-cooled evaporator 151 is communicated with the liquid-cooled plate of the battery pack 52 for cooling the battery pack 52. In the heat pump mode in the embodiment, the first throttling valve 22 needs to be disconnected, as in the embodiment of FIG. 6, to disconnect the bypass branch 20. The first expansion valve 14 can also be disconnected to disconnect the branch in which the first expansion valve 14 and the air-cooled evaporator 152 are located. The working principle of the compressor 12 refrigeration mode in the embodiment and the connection mode of the multi-way valve 80 are basically the same as those in the embodiment of FIG. 6. For details, refer to the embodiment of FIG. 6, which will not be described here.

[0174] It can be understood that in the heat pump mode in the embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened at the same time to communicate the branch in which the first expansion valve 14 and the air-cooled evaporator 152 are located.

[0175] FIG. 10 is a schematic diagram of another heat management system 1 provided in an embodiment of the application.

[0176] Referring to FIG. 10, in some embodiments, the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60 and the second pump branch 70 can refer to the bypass branch 20, the heat dissipation branch 40, the heat source branch 50, the first pump branch 60 and the second pump branch 70 in the embodiment of FIG. 1, which will not be described here. The main difference between the heat management system 1 in the embodiment and the heat management system 1 in the embodiment of FIG. 9 is that the structure of the main branch 10 is different.

[0177] Specifically, the first expansion valve 14 and the liquid-cooled evaporator 151 are connected in series through the first pipeline 11, the second expansion valve 17 and the air-cooled evaporator 152 are connected in series through the first pipeline 11, and the branch in which the first expansion valve 14 and the liquid-cooled evaporator 151 are located and the branch in which the second expansion valve 17 and the air-cooled evaporator 152 are located are connected in parallel. The output end of the bypass branch 20 is connected to the output end of the first expansion valve 14 and the input end of the liquid-cooled evaporator 151.

[0178] It can be understood that the heat management system 1 in the embodiment of FIG. 10 also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5) and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the modes are basically the same as those in the heat management system 1 in the embodiment of FIG. 1.

[0179] FIG. 10A is a schematic diagram of the mode of heating the battery pack 52 of the heat management system 1 in the embodiment of FIG. 10.

[0180] Compared with the mode of heating the battery pack 52 in the embodiments of FIG. 2 and FIG. 3, referring to FIG. 10A, this mode is also used when the ambient temperature where the battery pack 52 is located is less than the first threshold value or the temperature of the battery pack 52 is less than the second threshold value. In the mode of heating the battery pack 52 in this embodiment, since the second expansion valve 17 and the air-cooled evaporator 152 are additionally provided, the second expansion valve 17 and the air-cooled evaporator 152 need to be disconnected when the mode of heating the battery pack 52 is used, so as to avoid that the liquid refrigerant is contained in the refrigerant flowing from the second expansion valve 17 and the air-cooled evaporator 152 to the compressor 12, to control the suction superheat degree of the compressor 12 and improve the performance of the compressor 12. The working principle of the heat pump mode in this embodiment and the connection mode with the multi-way valve 80 are basically the same as those in the embodiments of FIG. 2 or FIG. 3. For details, please refer to the embodiments of FIG. 2 or FIG. 3, which will not be described here.

[0181] FIG. 10B is a schematic diagram of the heat pump mode of heating the battery pack 52 of the heat management system 1 in the embodiment of FIG. 10.

[0182] Referring to FIG. 10B, in the heat pump mode in this embodiment, the first throttle valve 22 needs to be disconnected, as in the embodiment of FIG. 4, to disconnect the bypass branch 20. The second expansion valve 17 can also be disconnected to disconnect the branch where the second expansion valve 17 and the air-cooled evaporator 152 are located. The working principle of the heat pump mode in this embodiment and the connection mode with the multi-way valve 80 are basically the same as those in the embodiment of FIG. 4. For details, please refer to the embodiment of FIG. 4, which will not be described here.

[0183] It can be understood that in the heat pump mode in this embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened at the same time, so that the branch where the second expansion valve 17 and the air-cooled evaporator 152 are located is also communicated.

[0184] FIG. 10C is a schematic diagram of the natural cooling mode of cooling the battery pack 52 of the heat management system 1 in the embodiment of FIG. 10.

[0185] Referring to FIG. 10C, in the natural cooling mode in this embodiment, the first expansion valve 14, the second expansion valve 17, the first throttle valve 22 and the second throttle valve 16 need to be disconnected at the same time, and the compressor 12 does not work. As for the working principle of the natural cooling mode in this embodiment and the connection mode with the multi-way valve 80, they are basically the same as those in the embodiment of FIG. 5. For details, please refer to the embodiment of FIG. 5, which will not be described here.

[0186] FIG. 10D is a schematic diagram of the compressor refrigeration mode of cooling the battery pack 52 of the heat management system 1 in the embodiment of FIG. 10.

[0187] Referring to FIG. 10D, in the heat pump mode of the present embodiment, the first throttling valve 22 needs to be disconnected to disconnect the bypass branch 20, as in the embodiment of FIG. 6. The second expansion valve 17 can also be disconnected to disconnect the branch in which the air-cooled evaporator 152 is located. The working principle of the compressor 12 in the refrigeration mode of the present embodiment and the connection mode with the multi-way valve 80 are basically the same as those in the embodiment of FIG. 6. For details, please refer to the embodiment of FIG. 6, which will not be described here.

[0188] It can be understood that in the heat pump mode of the present embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened at the same time to make the branch in which the air-cooled evaporator 152 is located also communicate.

[0189] FIG. 11 is a schematic diagram of another heat management system 1 provided by the present application.

[0190] Compared with the heat management system 1 in the embodiment of FIG. 9, referring to FIG. 11, the heat management system 1 in the present embodiment is not provided with the second throttling valve 16, and the other structures of the main trunk 10 are the same. For details, please refer to the embodiment of FIG. 9, which will not be described here. In the present embodiment, since the second throttling valve 16 is not provided, the proportion of the refrigerant flowing out of the output end of the compressor 12 to the condenser 13 and the bypass branch 20 can be adjusted by the first throttling valve 22, so as to effectively control the suction superheat degree of the compressor 12.

[0191] It can be understood that the heat management system 1 in the present embodiment also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5), and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the working modes are basically the same as those of the heat management system 1 in the embodiment of FIG. 1. For details, please refer to the embodiment of FIG. 1, which will not be described here.

[0192] FIG. 12 is a schematic diagram of another heat management system 1 provided by the present application.

[0193] Compared with the heat management system 1 in the embodiment of FIG. 10, referring to FIG. 12, the heat management system 1 in the present embodiment is not provided with the second throttling valve 16, and the other structures of the main trunk 10 are the same. For details, please refer to the embodiment of FIG. 10, which will not be described here.

[0194] It can be understood that the heat management system 1 in the present embodiment also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5), and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the working modes are basically the same as those of the heat management system 1 in the embodiment of FIG. 1. For details, please refer to the embodiment of FIG. 1, which will not be described here.

[0195] FIG. 13 is a schematic diagram of another heat management system 1 provided by the present application.

[0196] Compared with the heat management system 1 in the embodiment of FIG. 9, with reference to FIG. 13, the main difference between the heat management system 1 in the embodiment and the heat management system 1 in the embodiment of FIG. 9 is that, in the embodiment, a three-way throttling valve 90a is used to replace the first throttling valve 22 and the second throttling valve 16 in the embodiment of FIG. 9. The three-way throttling valve 90a can refer to the embodiment of FIG. 8, which will not be described here again.

[0197] It can be understood that the heat management system 1 in the embodiment also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5), and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the working modes in the heat management system 1 in the embodiment of FIG. 1 are basically the same, which will not be described here again.

[0198] FIG. 14 is a schematic diagram of another heat management system 1 provided by the embodiment of the application.

[0199] Compared with the heat management system 1 in the embodiment of FIG. 10, with reference to FIG. 14, the main difference between the heat management system 1 in the embodiment and the heat management system 1 in the embodiment of FIG. 10 is that, in the embodiment, a three-way throttling valve 90a is used to replace the first throttling valve 22 and the second throttling valve 16 in the embodiment of FIG. 10. The first throttling valve 22 and the second throttling valve 16 can refer to the embodiment of FIG. 8, which will not be described here again.

[0200] It can be understood that the heat management system 1 in the embodiment also includes the mode of heating the battery pack 52 (refer to FIG. 2 or FIG. 3), the heat pump mode (refer to FIG. 4), the natural heat dissipation mode (refer to FIG. 5), and the natural heat dissipation mode (refer to FIG. 6), and the working principles of the working modes in the heat management system 1 in the embodiment of FIG. 1 are basically the same, which will not be described here again.

[0201] FIG. 15 is a schematic diagram of another heat management system 1 provided by the embodiment of the application. For example, the heat management system 1 in the embodiment can be applied to a vehicle.

[0202] Compared with the heat management system 1 in the embodiment of FIG. 9, with reference to FIG. 15, the heat management system 1 in the embodiment has the following differences.

[0203] Referring to FIG. 15, in some embodiments, the multi-way valve 80 in the present embodiment has more interfaces than the multi-way valve 80 in the embodiment of FIG. 9. Specifically, the multi-way valve 80 includes a first interface, a second interface, a third interface, a fourth interface, a fifth interface, a sixth interface, a seventh interface, an eighth interface, and a ninth interface. The heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 are respectively connected to the first interface, the second interface, the third interface, the fourth interface, the fifth interface, the sixth interface, the seventh interface, the eighth interface, and the ninth interface of the multi-way valve 80, so as to realize integrated linkage of the heat dissipation branch 40, the heat source branch 50, the first pump branch 60, and the second pump branch 70 through the multi-way valve 80.

[0204] It is also to be noted that each interface of the multi-way valve 80 in the drawings is marked with a number. The first interface corresponds to the number 1 in the drawing, the second interface corresponds to the number 2 in the drawing, the third interface corresponds to the number 3 in the drawing, the fourth interface corresponds to the number 4 in the drawing, the fifth interface corresponds to the number 5 in the drawing, the sixth interface corresponds to the number 6 in the drawing, the seventh interface corresponds to the number 7 in the drawing, the eighth interface corresponds to the number 8 in the drawing, and the ninth interface corresponds to the number 9 in the drawing.

[0205] Referring to FIG. 15, in some embodiments, the number of the condensers 13 is plural. The plural condensers 13 include an air-cooled condenser 132 and a liquid-cooled condenser 131. The air-cooled condenser 132 is used for heat exchange between the refrigerant flowing through the air-cooled condenser 132 and the gas in the vehicle cabin. The liquid-cooled condenser 131 is used for heat exchange between the refrigerant flowing through the liquid-cooled evaporator 151 and other liquid flowing through the liquid-cooled evaporator 151. The liquid-cooled condenser 131 includes a first input end and a first output end in communication and a second input end and a second output end in communication. The evaporator 15 includes a first input end and a first output end in communication and a second input end and a second output end in communication. The compressor 12 is used for flowing the refrigerant to the bypass branch 20, the input end of the air-cooled condenser 132, and the first input end of the liquid-cooled condenser 131. The evaporator 15 is used for receiving the refrigerant flowing out of the bypass branch 20, the output end of the air-cooled condenser 132, and the first output end of the liquid-cooled condenser 131.

[0206] Specifically, the main trunk 10 in the present embodiment further has a third throttling valve 18 and an air-cooled condenser 132 compared with the main trunk 10 in the embodiment of FIG. 9. The third throttling valve 18 and the air-cooled condenser 132 are connected in series through the first pipeline 11. The third throttling valve 18 is used for controlling the flow of the refrigerant flowing to the air-cooled condenser 132. The air-cooled condenser 132 is used for heating the passenger cabin.

[0207] In this embodiment, the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 12 can not only flow to the bypass branch 20 where the first throttling valve 22 is located, but also flow to the second throttling valve 16 and the liquid-cooled condenser 131, and flow to the third throttling valve 18 and the air-cooled condenser 132. The refrigerant flowing out of the branch where the second throttling valve 16 and the liquid-cooled condenser 131 are located can flow to the branch where the first expansion valve 14 and the air-cooled evaporator 152 are located, or flow to the branch where the second expansion valve 17 and the liquid-cooled evaporator 151 are located.

[0208] Referring to FIG. 15, in some embodiments, the structure of the first pump branch 60 in this embodiment is different from that of the first pump branch 60 in the embodiment of FIG. 9.

[0209] The first pump branch 60 includes the fifth pipeline 61, the first pump 62, and the electric control assembly 64. The output end of the first pump 62 is in communication with the electric control assembly 64 and the second input end of the liquid-cooled condenser 131 through the fifth pipeline 61, that is, the electric control assembly 64 and the liquid-cooled condenser 131 are connected in parallel through the fifth pipeline 61. The liquid flowing out of the first pump 62 can flow to the electric control assembly 64 and the liquid-cooled evaporator 151. The liquid flowing out of the liquid-cooled evaporator 151 flows to the fifth interface, and the liquid flowing out of the electric control assembly 64 flows to the ninth interface. The second output end of the liquid-cooled condenser 131 is in communication with the fifth interface through the fifth pipeline 61, and the electric control assembly 64 is in communication with the ninth interface through the fifth pipeline 61. The input end of the first pump 62 is in communication with the sixth interface through the fifth pipeline 61.

[0210] Referring to FIG. 15, in some embodiments, the battery pack 52 in the heat source branch 50 in this embodiment is a vehicle-mounted battery.

[0211] It can be understood that the parts of the heat management system 1 not described in this embodiment can refer to the embodiment of FIG. 9, which will not be described here.

[0212] FIG. 15A is a schematic diagram of a mode of heating the battery pack 52 of the heat management system 1 in the embodiment of FIG. 15.

[0213] Referring to FIG. 15A, in some embodiments, the heat management system 1 includes a mode of heating the battery pack 52, which is mainly applied in a scenario where the ambient temperature is relatively low, such as when the ambient temperature of the vehicle is less than a first threshold value or the temperature of the battery pack 52 is less than a second threshold value. In this mode, the bypass branch 20 connects the output end of the compressor 12 and the input end of the liquid-cooled evaporator 151, the liquid-cooled condenser 131 is in communication with the liquid-cooled plate of the battery pack 52 for heating the battery pack 52, and the air-cooled condenser 132 is used for heating the passenger compartment. It should be noted that at this time, the ambient temperature of the vehicle is equivalent to the ambient temperature of the battery pack 52 of the vehicle, that is, the temperature of the atmosphere in the accommodating cavity where the battery pack 52 is placed.

[0214] Specifically, in the mode of heating the battery pack 52, the second interface of the multi-way valve 80 is in communication with the fifth interface and the ninth interface, respectively, and the sixth interface and the seventh interface. The second expansion valve 17 is disconnected to disconnect the branch in which the second expansion valve 17 and the liquid-cooled evaporator 151 are located, and the third throttle valve 18 is disconnected to disconnect the branch in which the third throttle valve 18 and the air-cooled condenser 132 are located.

[0215] At this time, the heat source branch 50 and the first pump branch 60 are in communication through the multi-way valve 80, the liquid (such as water) flowing out of the output end of the battery pack 52 flows through the seventh interface and the sixth interface to the input end of the first pump 62, and then flows from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and then flows from the second output end of the liquid-cooled condenser 131 to the fifth interface, the second interface, and finally to the input end of the battery pack 52, and so on. In the circulation process, the high-temperature gaseous refrigerant flowing from the output end of the compressor 12 to the liquid-cooled condenser 131 exchanges heat with the liquid flowing from the first water pump to the liquid-cooled condenser 131, so that the temperature of the liquid flowing to the battery pack 52 is increased, and the battery pack 52 can be heated. In addition, the liquid flowing out of the output end of the first pump 62 can also flow to the electronic control assembly 64, and then flow to the battery pack 52 through the ninth interface and the second interface. Since the liquid flowing from the output end of the first pump 62 to the electronic control assembly 64 is not heated by the liquid-cooled condenser 131, the electronic control assembly 64 will not be heated.

[0216] At the same time, part of the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 12 becomes low-temperature refrigerant after passing through the second throttle valve 16, the liquid-cooled condenser 131, and the first expansion valve 14, and flows to the air-cooled evaporator 152. Another part of the high-temperature gaseous refrigerant still flows to the air-cooled evaporator 152 after passing through the bypass branch 20 in which the first throttle valve 22 is located, and the high-temperature gaseous refrigerant and the low-temperature refrigerant are mixed in the air-cooled evaporator 152 to heat the low-temperature refrigerant, so as to control the suction superheat degree of the compressor 12, reduce the risk of liquid suction of the compressor 12, and improve the operation reliability of the compressor 12.

[0217] It can be understood that since the branch in which the second expansion valve 17 and the liquid-cooled evaporator 151 are located is disconnected, the refrigerant flowing out of the condenser 13 will not flow through the second expansion valve 17 and the liquid-cooled evaporator 151, and the bypass branch 20 is not connected to the branch in which the second expansion valve 17 and the liquid-cooled evaporator 151 are located. Therefore, the air-cooled evaporator 152 does not need to absorb heat from the external environment through the radiator 42 in the mode of heating the battery pack 52, so that in this embodiment, any connection mode between the first interface, the third interface, the fourth interface, and the eighth interface will not affect this mode. For example, in one connection mode, the first interface and the third interface can be in communication, and the fourth interface and the eighth interface can be in communication.

[0218] Fig. 15B is a schematic diagram of a heating cabin mode of the thermal management system 1 in the embodiment of Fig. 15.

[0219] Referring to Fig. 15B, in some embodiments, the thermal management system 1 comprises a heating cabin mode, which is mainly applied when the ambient temperature of the battery pack 52 is greater than the first threshold and the temperature of the battery pack 52 is greater than the second threshold, at this time, the bypass branch 20 is disconnected, and the output end of the compressor 12 and the input end of the liquid-cooled evaporator 151 are not communicated. The air-cooled condenser 132 is used to heat the cabin.

[0220] Specifically, in this mode, the second expansion valve 17 is disconnected to disconnect the branch in which the second expansion valve 17 and the liquid-cooled evaporator 151 are located, and the second throttle valve 16 is disconnected to disconnect the branch in which the second throttle valve 16 and the liquid-cooled condenser 131 are located.

[0221] The high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 12 is partially converted into low-temperature refrigerant after passing through the third throttle valve 18, the air-cooled condenser 132, and the first expansion valve 14, and flows to the air-cooled evaporator 152. When the high-temperature gaseous refrigerant flows through the air-cooled condenser 132, it can exchange heat with the air in the cabin to heat the cabin. Another part is still high-temperature gaseous refrigerant after passing through the bypass branch 20 in which the first throttle valve 22 is located, and flows to the air-cooled evaporator 152. In the air-cooled evaporator 152, the high-temperature gaseous refrigerant mixes with the low-temperature refrigerant to heat the low-temperature refrigerant, so as to control the suction superheat degree of the compressor 12, reduce the risk of liquid suction of the compressor 12, and improve the operation reliability of the compressor 12.

[0222] It can be understood that, since the second throttle valve 16 and the second expansion valve 17 are disconnected, the cooling liquid will not flow through the liquid-cooled condenser 131 and the liquid-cooled evaporator 151, so in this embodiment, any connection mode between the interfaces of the multi-way valve 80 will not affect this mode.

[0223] Fig. 15C is a schematic diagram of a heating battery pack 52 and cabin mode of the thermal management system 1 in the embodiment of Fig. 15.

[0224] Referring to Fig. 15C, in some embodiments, the thermal management system 1 comprises a heating battery pack 52 and cabin mode, which is mainly applied when the ambient temperature of the battery pack 52 is greater than the first threshold and the temperature of the battery pack 52 is greater than the second threshold, at this time, the bypass branch 20 is disconnected, and the output end of the compressor 12 and the input end of the liquid-cooled evaporator 151 are not communicated, the liquid-cooled condenser 131 is communicated with the liquid-cooled plate of the battery pack 52 to heat the battery pack 52, and the air-cooled condenser 132 is used to heat the cabin.

[0225] Specifically, in this mode, the second interface of the multi-way valve 80 is in communication with the fifth interface and the ninth interface, respectively, and the sixth interface and the seventh interface. The second expansion valve 17 is disconnected, so that the branch in which the second expansion valve 17 and the liquid-cooled evaporator 151 are located is disconnected, at this time, the heat source branch 50 and the first pump branch 60 are in communication through the multi-way valve 80, the liquid (such as water) flowing out of the output end of the battery pack 52 flows through the seventh interface, the sixth interface to the input end of the first pump 62, and then flows from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and flows from the second output end of the liquid-cooled condenser 131 to the fifth interface, the second interface, and finally to the input end of the battery pack 52, and so on. In the circulation process, the high-temperature gaseous refrigerant flowing from the output end of the compressor 12 to the liquid-cooled condenser 131 exchanges heat with the liquid flowing from the first water pump to the liquid-cooled condenser 131, so that the temperature of the liquid flowing to the battery pack 52 is increased, thereby heating the battery pack 52. In addition, the liquid flowing out of the output end of the first pump 62 can also flow to the electronic control assembly 64, and then flow to the battery pack 52 through the ninth interface and the second interface. Since the liquid flowing from the output end of the first pump 62 to the electronic control assembly 64 is not heated by the liquid-cooled condenser 131, the electronic control assembly 64 will not be heated.

[0226] At the same time, the first part of the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 12 passes through the third throttling valve 18, the air-cooled condenser 132 and the first expansion valve 14, becomes low-temperature refrigerant, and flows to the air-cooled evaporator 152. When the high-temperature gaseous refrigerant flows through the air-cooled condenser 132, it can exchange heat with the air in the passenger compartment to heat the passenger compartment. The second part of the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 12 passes through the second throttling valve 16, the liquid-cooled condenser 131 and the first expansion valve 14, becomes low-temperature refrigerant, and flows to the air-cooled evaporator 152. The high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 12 still has high temperature after passing through the bypass branch 20 in which the first throttling valve 22 is located, and flows to the air-cooled evaporator 152. In the air-cooled evaporator 152, the high-temperature gaseous refrigerant is mixed with the low-temperature refrigerant to heat the low-temperature refrigerant, so as to control the suction superheat degree of the compressor 12, reduce the risk of liquid suction of the compressor 12, and improve the operation reliability of the compressor 12.

[0227] It can be understood that since the branch in which the second expansion valve 17 and the liquid-cooled evaporator 151 are located is disconnected, in this embodiment, any connection mode between the first interface, the third interface, the fourth interface and the eighth interface will not affect this mode.

[0228] FIG. 15D is a schematic diagram of the heat pump heating battery and passenger compartment mode of the heat management system 1 in the embodiment of FIG. 15.

[0229] Referring to FIG. 15D, in some embodiments, the thermal management system 1 includes a heat pump heating battery and passenger cabin mode to heat the passenger cabin and the battery pack 52. This mode is mainly applied when the ambient temperature where the battery pack 52 is located is greater than a first threshold value and the temperature of the battery pack 52 is greater than a second threshold value, at this time, the bypass branch 20 is disconnected, the output end of the compressor 12 and the input end of the liquid-cooled evaporator 151 are not communicated, the liquid-cooled condenser 131 is communicated with the liquid-cooled plate of the battery pack 52 to heat the battery pack 52.

[0230] Specifically, in this mode, the first interface and the third interface are communicated, the fourth interface and the eighth interface are communicated to communicate the second pump branch 70 and the heat dissipation branch 40, the second interface is respectively communicated with the fifth interface and the ninth interface, and the sixth interface and the seventh interface are communicated to communicate the first pump branch 60 and the heat source branch 50. In addition, the first throttle valve 22 and the first expansion valve 14 are disconnected to disconnect the bypass branch 20 and the first expansion valve 14 and the branch where the air-cooled evaporator 152 is located.

[0231] At this time, part of the refrigerant flowing out of the compressor 12 flows through the second throttle valve 16, the liquid-cooled condenser 131, and the second expansion valve 17, becomes low-temperature refrigerant, and flows to the liquid-cooled evaporator 151, and the other part flows through the third throttle valve 18, the air-cooled condenser 132, and the second expansion valve 17, becomes low-temperature refrigerant, and when the high-temperature gaseous refrigerant flows through the air-cooled condenser 132, it can exchange heat with the air in the passenger cabin to heat the passenger cabin. Then the low-temperature refrigerant flows through the liquid-cooled evaporator 151 and returns to the compressor 12 again.

[0232] At this time, the second pump branch 70 and the heat dissipation branch 40 are communicated, so that the liquid (such as water) output from the heat sink 42 flows through the first interface, the third interface to the second pump 72, then flows through the second pump 72 to the second input end of the liquid-cooled evaporator 151, and then flows through the second output end of the liquid-cooled evaporator 151 to the eighth interface, the fourth interface, and finally to the heat sink 42, and so on. In the process of circulating the liquid, when passing through the liquid-cooled evaporator 151, it exchanges heat with the low-temperature refrigerant in the liquid-cooled evaporator 151, and the liquid flowing from the liquid-cooled evaporator 151 to the heat sink 42 is cooled, and when the liquid flowing through the heat sink 42, it can exchange heat with the external air to absorb the heat of the external air. In this process, the heat of the external air is used to heat the low-temperature refrigerant to make the refrigerant gaseous.

[0233] At this time, the heat source branch 50 and the first pump branch 60 are connected through the multi-way valve 80, the liquid (such as water) from the output end of the battery pack 52 flows through the seventh interface, the sixth interface to the input end of the first pump 62, then flows from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and flows from the second output end of the liquid-cooled condenser 131 to the fifth interface, the second interface, and finally to the input end of the battery pack 52, and so on. In the circulation process, the high-temperature gaseous refrigerant from the output end of the compressor 12 to the liquid-cooled condenser 131 exchanges heat with the liquid from the first water pump to the liquid-cooled condenser 131, so that the temperature of the liquid flowing to the battery pack 52 is increased, and the battery pack 52 can be heated. In addition, the liquid from the output end of the first pump 62 can also flow to the electronic control assembly 64, and then flow to the battery pack 52 through the ninth interface and the second interface. Since the liquid from the output end of the first pump 62 to the electronic control assembly 64 is not heated by the liquid-cooled condenser 131, the electronic control assembly 64 will not be heated.

[0234] FIG. 15E is a schematic diagram of a natural cooling mode of the thermal management system 1 in the embodiment of FIG. 15.

[0235] Referring to FIG. 15E, in some embodiments, the thermal management system 1 includes a natural cooling mode to naturally cool the battery pack 52 and the electronic control assembly 64. This mode is mainly applied when the ambient temperature of the environment where the battery pack 52 is located and the temperature of the battery pack 52 are both higher than those in the embodiment of FIG. 15D, and the battery pack 52 needs to be cooled. In this mode, the bypass branch 20 is disconnected, the output end of the compressor 12 and the input end of the liquid-cooled evaporator 151 are not connected, and the radiator 42 is connected to the liquid-cooled plate of the battery pack 52 to cool the battery pack 52.

[0236] Specifically, in the natural cooling mode, the first interface and the second interface are connected, the seventh interface and the sixth interface are connected, the ninth interface and the fifth interface are respectively connected to the third interface, the eighth interface and the fourth interface are connected, so that the heat source branch 50, the first pump branch 60, the second pump branch 70 and the cooling branch 40 are connected in series through the multi-way valve 80. In addition, at this time, the compressor 12 does not work.

[0237] In this mode, the liquid (such as water) flowing out of the output end of the battery pack 52 flows through the seventh interface, the sixth interface to the input end of the first pump 62, then flows from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and flows from the second output end of the liquid-cooled condenser 131 to the fifth interface, the third interface, to the input end of the second pump 72, then flows from the output end of the second pump 72 to the second input end of the liquid-cooled evaporator 151, and flows from the second output end of the liquid-cooled evaporator 151 to the eighth interface and the fourth interface, and flows to the input end of the radiator 42, then flows from the output end of the radiator 42 to the first interface and the second interface and to the battery pack 52, and so on. In this mode, the liquid flowing through the battery pack 52 exchanges heat with the heat generated by the battery pack 52, and the temperature of the liquid flowing out of the battery pack 52 is raised, and then exchanges heat with the air in the external environment when flowing through the radiator 42, so that the temperature of the liquid after flowing through the radiator 42 is lowered, thereby cooling the battery pack 52. In addition, the liquid flowing out of the output end of the first pump 62 can also flow to the electronic control assembly 64, and then flow to the battery pack 52 through the ninth interface and the second interface. Since the liquid flowing from the output end of the first pump 62 to the electronic control assembly 64 is in communication with the radiator 42, the electronic control assembly 64 can also be naturally cooled by the radiator 42. In this mode, since the compressor 12 does not work, the cooling of the battery pack 52 and the motor control by the radiator 42 in this mode can be achieved naturally, and since the compressor 12 does not work, the energy consumption can be effectively reduced.

[0238] FIG. 15F is a schematic diagram of the compressor 12 cooling mode of the thermal management system 1 in the embodiment of FIG. 15.

[0239] Referring to FIG. 15F, in some embodiments, the thermal management system 1 includes a compressor 12 cooling mode to cool the passenger compartment and the battery pack 52. This mode is mainly applied to the case where the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are both higher than those in the embodiment of FIG. 15E, and the battery pack 52 also needs to be cooled. In this mode, the bypass branch 20 is disconnected, the output end of the compressor 12 is not in communication with the input end of the liquid-cooled evaporator 151, the liquid-cooled evaporator 151 is in communication with the liquid-cooled plate of the battery pack 52 for cooling the battery pack 52, and the air-cooled evaporator 152 is used to cool the passenger compartment.

[0240] Specifically, in this mode, the first interface and the sixth interface are in communication, and the ninth interface, the fifth interface, and the fourth interface are in communication, so that the first pump branch 60 and the heat dissipation branch 40 are in communication. The second interface and the eighth interface are in communication, and the third interface and the seventh interface are in communication, so that the second pump branch 70 and the heat source branch 50 are in communication. In addition, the first throttle valve 22 and the third throttle valve 18 are disconnected, so that the bypass branch 20 and the branch where the air-cooled condenser 132 is located are disconnected.

[0241] At this time, the high-temperature gaseous refrigerant from the output end of the compressor 12 flows to the liquid-cooled condenser 131 through the second throttling valve 16, the refrigerant from the liquid-cooled condenser 131 flows to the first expansion valve 14 and the second expansion valve 17 respectively, and then flows to the air-cooled evaporator 152 and the liquid-cooled evaporator 151. The air-cooled evaporator 152 can exchange heat with the air in the passenger compartment to cool the passenger compartment, and the liquid-cooled evaporator 151 can cool the liquid (such as water) flowing to the liquid-cooled evaporator 151 from the second pump 72 to cool the battery pack 52.

[0242] At the same time, the first pump branch 60 and the heat dissipation branch 40 are connected, so that the heat generated by the electronic control assembly 64 can be dissipated to the environment outside the passenger compartment through the radiator 42 to achieve heat dissipation of the electronic control assembly 64.

[0243] FIG. 16 is a schematic diagram of another heat management system 1 provided by an embodiment of the present application.

[0244] Compared with the heat management system 1 in the embodiment of FIG. 15, with reference to FIG. 16, the main difference between the heat management system 1 of the present embodiment and the heat management system 1 in the embodiment of FIG. 15 is that the first throttling valve 22, the second throttling valve 16 and the third throttling valve 18 in the embodiment of FIG. 15 are replaced by a four-way throttling valve 90b in the present embodiment.

[0245] Specifically, the four-way throttling valve 90b includes a first interface, a second interface, a third interface and a fourth interface. The first interface is connected with the output end of the compressor 12 through the first pipeline 11, the second interface is connected with the input end of the liquid-cooled condenser 131 through the first pipeline 11, the third interface is connected with the input end of the air-cooled condenser 132 through the first pipeline 11, and the fourth interface is connected with the input end of the bypass branch 20 through the first pipeline 11. In the present embodiment, the use of the four-way throttling valve 90b instead of the first throttling valve 22, the second throttling valve 16 and the third throttling valve 18 can reduce the number of valves, thereby simplifying the control system, reducing the failure rate, and possibly reducing the overall cost.

[0246] It can be understood that the four-way throttling valve 90b in the present embodiment includes the function of throttling, and can control the flow through the first interface, the second interface, the third interface and the fourth interface. In some embodiments, the four-way throttling valve 90b can be a four-way expansion valve, which has the function of throttling and pressure reduction.

[0247] FIG. 17 is a schematic diagram of another heat management system 1 provided by an embodiment of the present application.

[0248] Compared with the heat management system 1 in the embodiment of FIG. 16, referring to FIG. 17, the main difference between the heat management system 1 in the embodiment and the heat management system 1 in the embodiment of FIG. 16 is that the output end of the bypass branch 20 is connected between the input end of the liquid cooling evaporator 151 and the output end of the second expansion valve 17 in the embodiment. The working principle of the heat management system 1 in the embodiment can refer to the embodiment of FIG. 16, which will not be repeated here.

[0249] FIG. 18 is a schematic diagram of another heat management system 1 provided by the embodiments of the present application.

[0250] Compared with the heat management system 1 in the embodiment of FIG. 15, referring to FIG. 18, the main difference between the heat management system 1 in the embodiment and the heat management system 1 in the embodiment of FIG. 18 is that the first throttle valve 22 and the third throttle valve 18 in the embodiment of FIG. 15 are replaced by a three-way throttle valve 90a in the embodiment. In the embodiment, using a four-way throttle valve 90b to replace the first throttle valve 22, the second throttle valve 16 and the third throttle valve 18 can reduce the number of valves, thereby simplifying the control system, reducing the failure rate, and possibly reducing the overall cost.

[0251] It can be understood that the three-way throttle valve 90a in the embodiment includes the function of throttling, which can control the flow through the first interface, the second interface and the third interface. In some embodiments, the three-way throttle valve 90a can be a three-way expansion valve, which has the function of throttling and pressure reduction.

[0252] FIG. 19 is a schematic diagram of another heat management system 1 provided by the embodiments of the present application.

[0253] Compared with the heat management system 1 in the embodiment of FIG. 18, referring to FIG. 19, the main difference between the heat management system 1 in the embodiment and the heat management system 1 in the embodiment of FIG. 18 is that the output end of the bypass branch 20 is connected between the input end of the liquid cooling evaporator 151 and the output end of the second expansion valve 17 in the embodiment. The working principle of the heat management system 1 in the embodiment can refer to the embodiment of FIG. 18, which will not be repeated here.

[0254] It should be noted that when the heat management system 1 in the above-mentioned embodiments is applied in the energy storage cabinet, the environment temperature of the battery pack 52 is equivalent to the environment temperature of the energy storage cabinet, that is, the atmosphere temperature in the inner cavity of the cabinet body of the energy storage cabinet for placing the battery pack 52, which can be detected by a sensor. Similarly, when the heat management system 1 in the above-mentioned embodiments is applied in the vehicle, the environment temperature of the battery pack 52 is equivalent to the environment temperature of the vehicle, that is, the atmosphere temperature in the accommodating cavity of the vehicle for placing the battery pack 52, which can also be detected by a sensor.

[0255] The above merely provides the specific implementation of the present application, but the protection scope of the present application is not limited to this. Any person skilled in the art can easily think of the changes or replacements within the technical range disclosed by the present application, which should be covered in the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A thermal management system for dissipating heat from a battery pack, the system comprising: The heat management system selectively connects at least one of an input end of the bypass branch or an input end of the condenser to an output end of the compressor. The bypass branch includes a first throttling valve disposed on the bypass branch, the first throttling valve being configured to open or close the bypass branch, or to regulate a flow rate of the refrigerant from the output end of the compressor to the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator.

2. The thermal management system of claim 1, wherein, The heat management system further includes a multi-way throttling valve, the multi-way throttling valve including a first interface, a second interface, and a third interface; 3. The thermal management system of claim 1 or 2, wherein, The first interface is configured to communicate with the output end of the compressor; The second interface is configured to communicate with the input end of the condenser, and to control a flow rate of the refrigerant from the compressor to the condenser; The third interface is configured to communicate with the input end of the bypass branch, and to control a flow rate of the refrigerant from the compressor to the bypass branch. The heat management system further includes a second throttling valve configured to control a flow rate of the refrigerant from the compressor to the condenser.

4. The thermal management system of claim 1 or 2, wherein, When an ambient temperature of an environment in which the battery pack is located is less than a first threshold value or a temperature of the battery pack is less than a second threshold value, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch, and the compressor inputs the refrigerant to the condenser and outputs the refrigerant from the condenser.

5. The thermal management system of any of claims 1-4, wherein, The heat management system further includes a heat sink, 6. The thermal management system of any of claims 1-5, wherein, When the ambient temperature of the environment in which the battery pack is located is T1, or the temperature of the battery pack is T2, the condenser communicates with a liquid-cooled plate of the battery pack to heat the battery pack, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch, and the compressor inputs the refrigerant to the condenser and outputs the refrigerant from the condenser; When the ambient temperature of the environment in which the battery pack is located is T3, and the temperature of the battery pack is T4, the bypass branch is disconnected, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant output from the condenser, and the heat sink is configured to dissipate heat from the battery pack; When the ambient temperature of the environment in which the battery pack is located is T5, or the temperature of the battery pack is T6, the bypass branch is disconnected, the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator receives the refrigerant output from the condenser, at least one of the liquid-cooled evaporator or the air-cooled evaporator communicates with a liquid-cooled plate of the battery pack, and at least one of the liquid-cooled evaporator or the air-cooled evaporator is configured to cool the battery pack. ​ Wherein, T1 < the first threshold value < T3 < T5, T2 < the second threshold value < T4 < T6.

7. The thermal management system of any of claims 1-6, wherein, The bypass branch includes a first throttling valve arranged on the bypass branch, the first throttling valve being configured to open or close the bypass branch, or to adjust the flow rate of the refrigerant input from the compressor output end to at least one input end of the liquid-cooled evaporator or air-cooled evaporator through the bypass branch; the thermal management system further includes a sensor configured to detect at least one of the temperature and pressure of the refrigerant input to the compressor, and a controller configured to control the first throttling valve to adjust the flow rate of the refrigerant input from the compressor output end to at least one input end of the liquid-cooled evaporator or air-cooled evaporator through the bypass branch according to at least one of the temperature and pressure of the refrigerant input to the compressor detected by the sensor.

8. The thermal management system of claim 7, wherein, The controller is configured to control the first throttling valve to adjust the flow rate of the refrigerant input from the compressor output end to at least one input end of the liquid-cooled evaporator or air-cooled evaporator through the bypass branch according to at least one of the temperature and pressure of the refrigerant input to the compressor, the ambient temperature where the battery pack is located, or the temperature of the battery pack detected by the sensor.

9. An energy storage device, characterized by, The energy storage device includes a battery pack and the thermal management system according to any one of claims 1-8, the thermal management system being configured to adjust the temperature of the battery pack or to adjust the temperature of the energy storage device.

10. The energy storage device of claim 9, wherein, When the ambient temperature where the energy storage device is located is less than the first threshold value or the temperature of the battery pack is less than the second threshold value, at least one input end of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch, and the compressor inputs the refrigerant to the condenser and outputs the refrigerant from the condenser.

11. Energy storage device according to claim 9 or 10, characterized in that The energy storage device further includes a power module configured to perform power conversion on the electrical energy output by the battery pack, and a second input end and a second output end of at least one of the liquid-cooled evaporator or air-cooled evaporator are configured to communicate with a liquid-cooled plate of the power module to dissipate heat for the power module.

12. The energy storage device of any one of claims 9-11, wherein, The energy storage device is an energy storage cabinet or a vehicle powered by the battery pack.

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