Thermal management system for heat dissipation of battery pack and energy storage equipment

Abstract

The utility model provides a heat management system for heat dissipation of a battery pack and energy storage equipment, and the output end of a compressor in the heat management system communicates with a condenser, is connected with an evaporator, and is directly connected with the input end of the evaporator through a bypass branch. The input end of the evaporator selectively receives a low-temperature refrigerant from the condenser and a high-temperature gaseous refrigerant from the compressor, and the low-temperature refrigerant and the high-temperature gaseous refrigerant are mixed in the evaporator, so that the low-temperature refrigerant is heated by the high-temperature gaseous refrigerant, and therefore, in a low-temperature environment, the degree of superheat of the refrigerant flowing out of the evaporator can be effectively improved; the compressor is prevented from sucking liquid refrigerants under the low-temperature condition, the risk that the compressor sucks air and carries liquid is eliminated, and therefore the operation reliability of the compressor in the low-temperature state can be improved.

Description

Technical Field

[0001] This application relates to the technical field of thermal management, and more particularly to a thermal management system and energy storage device for dissipating heat from a battery pack. Background Technology

[0002] In the thermal management system of related technologies, when the temperature of the application environment is relatively low, the temperature of the refrigerant flowing from the condenser to the evaporator is low. Even after absorbing heat in the evaporator, it still cannot be effectively converted into gaseous refrigerant. As a result, the gaseous refrigerant flowing out of the evaporator and into the compressor contains liquid refrigerant, which leads to poor operating stability and short service life of the compressor. Utility Model Content

[0003] Embodiments of this application provide a thermal management system and energy storage device for dissipating heat from a battery pack, thereby improving the operational stability of the compressor when the ambient temperature is low.

[0004] In the first aspect, the refrigerant output from the compressor in the thermal management system selectively enters at least one of the liquid-cooled evaporator or the air-cooled evaporator through at least one of the bypass branch or the condenser. The output end of the compressor is used to connect the input end of the bypass branch and the input end of the condenser, respectively. The output end of the bypass branch and the output end of the condenser are used to supply refrigerant to the input end of at least one of the liquid-cooled evaporator or the air-cooled evaporator. The thermal management system is used to selectively connect at least one of the input end of the bypass branch or the input end of the condenser and the output end of the compressor.

[0005] Liquid-cooled evaporators are used to cool the battery pack by exchanging heat between the refrigerant flowing through them and the liquid cooling plate, while air-cooled evaporators are used to exchange heat between the refrigerant flowing through them and the air in the environment where the battery pack is located.

[0006] In this embodiment, a portion of the high-temperature, high-pressure gaseous refrigerant flowing from the compressor output flows out through the condenser, while the other portion flows out through a bypass branch. The refrigerant flowing out through the condenser is at a lower temperature and contains a large amount of liquid refrigerant, while the refrigerant flowing out through the bypass branch remains a high-temperature gaseous refrigerant because it has not passed through the condenser. By selectively connecting at least one of the input ends of the bypass branch and the condenser to the compressor output end, both the low-temperature refrigerant flowing out through the condenser and the high-temperature refrigerant flowing out through the bypass branch flow to the evaporator (at least one of a liquid-cooled evaporator or an air-cooled evaporator), effective mixing can be achieved within the evaporator. The high-temperature and low-temperature refrigerants undergo sufficient heat exchange within the evaporator, effectively heating the refrigerant flowing into the evaporator from the condenser. This effectively increases the superheat of the refrigerant at the evaporator outlet, ensuring that the refrigerant entering the compressor has a certain suction superheat. Consequently, in low-temperature environments, the risk of liquid carryover during compressor suction can be effectively reduced or eliminated, improving the reliability of compressor operation. In addition, since the thermal management system in this embodiment makes full use of the compressor required by the thermal management system, only one bypass branch is added. This can effectively improve the compressor suction superheat in low temperature environments, improve the compressor's operational reliability, and also effectively save costs and improve competitiveness.

[0007] In some embodiments, the compressor is selectively used to supply refrigerant to the bypass branch and the condenser, respectively. At least one of the liquid-cooled evaporator or air-cooled evaporator is selectively used to receive refrigerant flowing from the bypass branch and refrigerant flowing from the condenser, and to supply refrigerant to the compressor. In this embodiment, both the low-temperature refrigerant flowing out of the condenser and the high-temperature refrigerant flowing out of the bypass branch flow to at least one of the liquid-cooled evaporator or air-cooled evaporator, thereby enabling effective mixing within at least one of the liquid-cooled evaporator or air-cooled evaporator. This allows the refrigerant flowing into at least one of the liquid-cooled evaporator or air-cooled evaporator to be effectively heated, effectively increasing the refrigerant superheat at the outlet of at least one of the liquid-cooled evaporator or air-cooled evaporator. This ensures that the refrigerant entering the compressor has a certain suction superheat, thereby effectively reducing or eliminating the risk of liquid carryover during compressor suction in low-temperature environments and improving the reliability of compressor operation.

[0008] In some embodiments, the bypass branch includes a first throttling valve disposed on the bypass branch. The first throttling valve is used to open or close the bypass branch, or to regulate the flow rate of refrigerant input from the compressor output to at least one input of the liquid-cooled evaporator or air-cooled evaporator via the bypass branch. In this embodiment, because the first throttling valve can control the flow rate of refrigerant through the bypass branch, the flow rate can be adjusted in different application scenarios to regulate the ratio of low-temperature refrigerant flowing out of the condenser to high-temperature gaseous refrigerant flowing out of the first throttling valve. This, in turn, controls the compressor's suction superheat, reduces the risk of liquid carryover during suction, and improves the compressor's operational reliability. The thermal management system in this embodiment can adapt to a wider range of application scenarios.

[0009] In some embodiments, the thermal management system further includes a multi-way throttle valve, which includes a first interface, a second interface, and a third interface;

[0010] The first interface is used to connect to the output end of the compressor;

[0011] The second interface is used to connect to the input end of the condenser and to control the flow rate of refrigerant from the compressor to the condenser;

[0012] The third interface is used to connect to the input of the bypass branch and to control the flow rate of refrigerant from the compressor to the bypass branch.

[0013] In this embodiment, using a multi-way throttle valve instead of the first and second throttle valves can reduce the number of valves, thereby simplifying the control system, reducing the failure rate, and potentially reducing the overall cost.

[0014] In some embodiments, the thermal management system further includes a second throttling valve, which is installed on the pipeline connecting the output end of the compressor and the input end of the condenser. The second throttling valve is used to control the flow rate of refrigerant from the compressor to the condenser. In this embodiment, by controlling the flow rate of the second throttling valve, the flow rate of the high-temperature, high-pressure gaseous refrigerant from the output end of the compressor to the condenser can be controlled. Similarly, the ratio of low-temperature refrigerant flowing out of the output end of the condenser to high-temperature gaseous refrigerant flowing out of the bypass branch can be controlled to ensure that the refrigerant entering the compressor has a certain suction superheat, thereby reducing the risk of liquid carryover during suction and improving the reliability of compressor operation.

[0015] In some embodiments, when the ambient temperature of the battery pack is lower than a first threshold or the battery pack temperature is lower than a second threshold, the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives refrigerant transmitted by the compressor through a bypass branch, as well as refrigerant input by the compressor to the condenser and output by the condenser. That is, the compressor simultaneously receives refrigerant transmitted through the bypass branch and refrigerant flowing out of the condenser. In this embodiment, when the ambient temperature of the battery pack is lower than the first threshold or the battery pack temperature is lower than the second threshold, the bypass branch connects the output terminal of the compressor to the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator. This allows the high-temperature gaseous refrigerant output by the compressor to be transported to at least one of the liquid-cooled evaporator or air-cooled evaporator via the bypass branch, mixing and heating with the low-temperature refrigerant transported by the condenser to at least one of the liquid-cooled evaporator or air-cooled evaporator. This effectively solves the problem of liquid carryover temperature in the compressor's suction flow under low-temperature conditions, improving the compressor's operational reliability. It is understood that when the ambient temperature is high, such as when the ambient temperature of the battery pack is higher than the first threshold and the battery pack temperature is higher than the second threshold, the bypass branch can be disconnected, while still ensuring the compressor's operational stability.

[0016] In some embodiments, the thermal management system also includes a radiator.

[0017] When the ambient temperature of the battery pack is T1, or the temperature of the battery pack is T2, the condenser is connected to the liquid cooling plate of the battery pack to provide heating for the battery pack. The input end of at least one of the liquid cooling evaporator or air cooling evaporator receives the refrigerant transmitted by the compressor through the bypass branch, as well as the refrigerant input by the compressor to the condenser and output by the condenser.

[0018] When the ambient temperature of the battery pack is T3 and the temperature of the battery pack is T4, the heat sink is connected to the liquid cooling plate of the battery pack to dissipate heat from the battery pack.

[0019] When the ambient temperature of the battery pack is T5, or the temperature of the battery pack is T6, the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant output from the condenser, at least one of the liquid-cooled evaporator or air-cooled evaporator is connected to the liquid cooling plate of the battery pack, and at least one of the liquid-cooled evaporator or air-cooled evaporator is used to cool the battery pack.

[0020] Where T1 < first threshold < T3 < T5, T2 < second threshold < T4 < T6.

[0021] In this embodiment, when the ambient temperature of the battery pack is T1 or the temperature of the battery pack is T2, and the temperature of T1 is less than the first threshold and the temperature of T2 is less than the second threshold, under this temperature environment, a portion of the high-temperature gaseous refrigerant flowing out of the compressor flows to the condenser to exchange heat with the liquid in the liquid cooling plate of the battery pack through the condenser, and also heats the battery pack. The other portion of the high-temperature gaseous refrigerant flowing out of the compressor flows to at least one of the liquid-cooled evaporator or air-cooled evaporator through a bypass branch, mixing and heating the refrigerant flowing from the condenser to at least one of the liquid-cooled evaporator or air-cooled evaporator. This effectively reduces the risk of liquid carryover in the compressor's suction in a low-temperature environment and improves the operating stability of the compressor. When the ambient temperature of the battery pack is T3 and the battery pack temperature is T4, where T3 is greater than the first threshold and T4 is greater than the second threshold, the ambient temperature will not drop to the point where the compressor cannot operate stably. Therefore, the bypass branch is disconnected, and the battery pack can be cooled by connecting the radiator to the liquid cooling plate, eliminating the need for the compressor and effectively reducing energy consumption. However, when the temperature rises further, such as to T5 or T6, the compressor needs to operate. At least one of the liquid-cooled or air-cooled evaporators is connected to the liquid cooling plate of the battery pack to dissipate heat. Because the temperature is high enough, the proportion of liquid refrigerant flowing out of at least one of the liquid-cooled or air-cooled evaporators will not be too high. Therefore, it is not necessary to use the bypass branch to redirect a portion of the high-temperature refrigerant flowing from the compressor to at least one of the liquid-cooled or air-cooled evaporators.

[0022] In some embodiments, the thermal management system further includes sensors and a controller. The sensors detect at least one of the temperature and pressure of the refrigerant input to the compressor. The controller controls a first throttle valve to regulate the flow rate of refrigerant entering from the compressor output through a bypass branch to at least one input of either a liquid-cooled evaporator or an air-cooled evaporator, based on the temperature and pressure of the refrigerant detected by the sensors. In this embodiment, the sensors can monitor the temperature and pressure of the refrigerant entering the compressor in real time, thereby enabling real-time monitoring of the compressor's suction superheat. The controller then controls the flow rate of the first throttle valve based on the information fed back from the sensors to dynamically control the compressor's suction superheat, reduce the risk of liquid carryover during suction, and improve the compressor's operational reliability.

[0023] In some embodiments, the controller is used to control the first throttle valve to regulate the flow rate of refrigerant input from the compressor output to at least one input terminal of the liquid-cooled evaporator or the air-cooled evaporator via a bypass branch, based on at least one of the refrigerant temperature and pressure input to the compressor detected by sensors, the ambient temperature of the battery pack, or the temperature of the battery pack. In this embodiment, the flow rate of the first throttle valve can be controlled not only by monitoring at least one of the refrigerant temperature or pressure input to the compressor, but also by monitoring at least one of the ambient temperature of the battery pack or the temperature of the battery pack, thereby improving fault tolerance.

[0024] Secondly, embodiments of this application provide an energy storage device, which includes a battery pack and a thermal management system as described in any of the first aspects. The thermal management system is used to regulate the temperature of the battery pack or the temperature of the energy storage device. Because the energy storage device in this embodiment includes a thermal management system that provides good stability in low-temperature environments, it can operate stably in low-temperature environments.

[0025] In some embodiments, when the ambient temperature of the energy storage device is lower than a first threshold or the battery pack temperature is lower than a second threshold, the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives refrigerant transmitted by the compressor through a bypass branch, as well as refrigerant input by the compressor to the condenser and output by the condenser. That is, the compressor simultaneously receives refrigerant transmitted through the bypass branch and refrigerant flowing out of the condenser. In this embodiment, when the ambient temperature of the energy storage device is lower than the first threshold or the battery pack temperature is lower than the second threshold, because the bypass branch connects the output terminal of the compressor to the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator, the compressor's suction superheat can be controlled, reducing the risk of liquid carryover during compressor suction, thereby improving the operational stability of the energy storage device.

[0026] In some embodiments, the energy storage device further includes a power module for power conversion of the electrical energy output from the battery pack. A second input terminal and a second output terminal of at least one of a liquid-cooled evaporator or an air-cooled evaporator are connected to the liquid-cooled plate of the power module for heat dissipation. In this embodiment, cooling the power module can be achieved through at least one of the liquid-cooled evaporator or air-cooled evaporator, thereby ensuring the stable operation of the power module and thus the stable operation of the energy storage device.

[0027] In some embodiments, the energy storage device is an energy storage cabinet or a vehicle powered by a battery pack. Attached Figure Description

[0028] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below.

[0029] Figure 1 This is a schematic diagram of the structure of a thermal management system provided in an embodiment of this application;

[0030] Figure 2 for Figure 1 One of the schematic diagrams of the heating battery pack mode of the thermal management system in the embodiment;

[0031] Figure 3 for Figure 1 Another schematic diagram of the heating battery pack mode of the thermal management system in the embodiment;

[0032] Figure 4 for Figure 1 A schematic diagram of the heat pump mode heating of the battery pack in the embodiment of the thermal management system;

[0033] Figure 5 for Figure 1 A schematic diagram of the natural heat dissipation mode of the thermal management system in the embodiment for cooling the battery pack;

[0034] Figure 6 for Figure 1 A schematic diagram of the compressor cooling mode of the thermal management system in the embodiment for cooling the battery pack;

[0035] Figure 7 A schematic diagram of another thermal management system provided in an embodiment of this application;

[0036] Figure 8 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0037] Figure 9 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0038] Figure 9A for Figure 9 A schematic diagram of the heating battery pack mode of the thermal management system in the embodiment;

[0039] Figure 9B for Figure 9 A schematic diagram of the heat pump mode heating of the battery pack in the embodiment of the thermal management system;

[0040] Figure 9C for Figure 9 A schematic diagram of the natural heat dissipation mode of the thermal management system in the embodiment for cooling the battery pack;

[0041] Figure 9D for Figure 9 A schematic diagram of the compressor cooling mode of the thermal management system in the embodiment for cooling the battery pack;

[0042] Figure 10 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0043] Figure 10A for Figure 10 A schematic diagram of the heating battery pack mode of the thermal management system in the embodiment;

[0044] Figure 10B for Figure 10 A schematic diagram of the heat pump mode heating of the battery pack in the embodiment of the thermal management system;

[0045] Figure 10C for Figure 10 A schematic diagram of the natural heat dissipation mode of the thermal management system in the embodiment for cooling the battery pack;

[0046] Figure 10D for Figure 10 A schematic diagram of the compressor cooling mode of the thermal management system in the embodiment for cooling the battery pack;

[0047] Figure 11 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0048] Figure 12 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0049] Figure 13 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0050] Figure 14 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0051] Figure 15 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0052] Figure 15A for Figure 15 A schematic diagram of the heating battery pack mode of the thermal management system in the embodiment;

[0053] Figure 15B for Figure 15 A schematic diagram of the heated passenger compartment mode of the thermal management system in the embodiment;

[0054] Figure 15C for Figure 15 A schematic diagram of the heated battery pack and crew cabin mode of the thermal management system in the embodiment;

[0055] Figure 15D for Figure 15 A schematic diagram of the thermal management system's heat pump heating battery and crew cabin mode in the embodiment;

[0056] Figure 15E for Figure 15A schematic diagram of the natural heat dissipation mode of the thermal management system in the embodiment;

[0057] Figure 15F for Figure 15 A schematic diagram of the compressor cooling mode of the thermal management system in the embodiment;

[0058] Figure 16 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0059] Figure 17 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0060] Figure 18 A schematic diagram of yet another thermal management system provided in an embodiment of this application;

[0061] Figure 19 This is a schematic diagram of another thermal management system provided in an embodiment of this application.

[0062] Explanation of reference numerals in the attached figures:

[0063] 1. Thermal management system;

[0064] 10. Main pipeline; 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;

[0065] 20. Bypass branch; 21. Second pipeline; 22. First throttle valve;

[0066] 31. Sensor; 32. Controller;

[0067] 40. Heat dissipation branch; 41. Third pipe; 42. Radiator;

[0068] 50. Heat source branch; 51. Fourth pipeline; 52. Battery pack;

[0069] 60. First pump branch; 61. Fifth pipeline; 62. First pump; 63. Power module; 64. Electronic control assembly;

[0070] 70. Second pump branch; 71. Sixth pipeline; 72. Second pump;

[0071] 80. Multi-way valve;

[0072] 90. Multi-way throttle valve; 91. First port; 92. Second port; 93. Third port; 90a. Three-way throttle valve; 90b. Four-way throttle valve. Detailed Implementation

[0073] The following section will first explain some of the terms used in the embodiments of this application.

[0074] The terms "first," "second," "third," "fourth," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented, for example, in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0075] This application provides an energy storage device, which is an energy storage cabinet or a vehicle powered by a battery pack.

[0076] The energy storage device includes a battery pack and a thermal management system, which regulates the temperature of the battery pack or the energy storage device itself. The thermal management system of the energy storage device in this embodiment exhibits good operational stability in low-temperature environments. The energy storage cabinet and the vehicle are described below.

[0077] Energy storage cabinets can be industrial and commercial energy storage cabinets, power plant energy storage cabinets, or containerized energy storage cabinets, etc.

[0078] For energy storage cabinets, the cabinet includes the cabinet body and the battery pack and thermal management system located inside the cabinet. The thermal management system is used for thermal management of the battery pack, such as cooling or heating it. For some energy storage cabinets, such as industrial and commercial energy storage cabinets, the thermal management system is also used for thermal management of the cabinet's internal cavity, such as dehumidification, cooling, or heating. Of course, for some energy storage cabinets, power modules are also included, and the thermal management system can also be used for thermal management of the power modules in the energy storage cabinet.

[0079] Specifically, the thermal management system can perform heat exchange on the liquid cooling plates of the battery pack to achieve thermal management of the battery pack. Power modules may include power converters and cluster control boxes, etc.

[0080] However, some energy storage cabinets in related technologies exhibit poor operational stability and reduced service life of their thermal management systems when the ambient temperature is low. This is because, at low ambient temperatures, the liquid refrigerant flowing from the condenser to the evaporator in the thermal management system cannot absorb enough heat as it passes through the evaporator. Consequently, it cannot effectively transform into gaseous refrigerant when flowing out of the evaporator. As a result, the gaseous refrigerant flowing out of the evaporator and into the compressor contains liquid refrigerant, which makes it impossible to effectively control the superheat of the compressor's suction, leading to poor compressor operational stability and a short service life.

[0081] To address the issue of poor operational stability of the thermal management system at low ambient temperatures, the energy storage cabinet in this embodiment provides a novel thermal management system architecture. By rationally and effectively utilizing the compressor required in the thermal management system, the high-temperature gaseous refrigerant flowing out of the compressor effectively supplements the heat of the refrigerant flowing from the condenser to the evaporator. This effectively reduces the proportion of liquid refrigerant in the refrigerant flowing out of the evaporator, thereby effectively controlling the compressor's suction superheat and improving the compressor's operational stability and service life. Consequently, the operational stability and service life of the thermal management system of the energy storage cabinet can be effectively improved at low ambient temperatures.

[0082] For a vehicle, the vehicle includes an in-vehicle infotainment system, a battery pack located within the infotainment system, and a thermal management system. The infotainment system includes a cabin for carrying passengers or cargo. The thermal management system is used to manage the thermal of its electronic control assembly and on-board battery. The thermal management system can also manage the thermal of the vehicle's passenger compartment to achieve heating and cooling of the compartment.

[0083] Electronic control assemblies and vehicle batteries each have specific operating temperatures. For example, vehicle batteries typically maintain stable performance and longer battery life within a temperature range of 0℃-60℃. A thermal management system can manage the operating temperatures of these components, ensuring they operate within suitable temperature ranges. This improves their performance, resulting in lower power consumption and a longer lifespan for the vehicle.

[0084] A vehicle battery is a battery used to provide electrical energy to a vehicle, and can be a lithium-ion battery, lead-acid battery, nickel-cadmium battery, nickel-metal hydride battery, or sodium-ion battery, etc.

[0085] The vehicles provided in this application embodiment may include, but are not limited to, electric vehicles / electric cars, pure electric vehicles, hybrid electric vehicles, range-extended electric vehicles, plug-in hybrid electric vehicles, and new energy vehicles.

[0086] Specifically, the electronic control assembly and the vehicle battery can be placed on a liquid cooling plate so that the thermal management system can be used to dissipate heat, heat or keep the electronic control assembly and the vehicle battery warm.

[0087] In vehicles using related technologies, when the operating environment is in a low temperature, such as during the harsh winter in the north, the thermal management system in the vehicle, like the energy storage cabinet, suffers from poor operational stability and a short service life.

[0088] To address the issue of poor operational stability of the thermal management system at low ambient temperatures, the vehicle in this embodiment provides a novel thermal management system architecture identical to that in the energy storage cabinet.

[0089] The vehicle features a novel thermal management system that effectively utilizes the high-temperature gaseous refrigerant flowing from the compressor to supplement the refrigerant flowing from the condenser to the evaporator. This effectively reduces the proportion of liquid refrigerant in the refrigerant flowing from the evaporator, thereby effectively controlling the compressor's suction superheat and improving the compressor's operational stability and lifespan. Consequently, it can effectively improve the operational stability and lifespan of the vehicle's thermal management system when the ambient temperature is low.

[0090] The following section will focus on a thermal management system that can effectively improve the operational stability and service life of energy storage cabinets and vehicles when the ambient temperature is low.

[0091] Figure 1 This is a schematic diagram of the structure of a thermal management system 1 provided in an embodiment of this application.

[0092] Reference Figure 1 The thermal management system 1 includes a compressor 12, a condenser 13, an evaporator 15, and a bypass branch 20. The compressor 12, condenser 13, and evaporator 15 are connected in series via piping. 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 low-pressure gaseous refrigerant into a high-pressure gaseous refrigerant. The high-pressure gaseous refrigerant is liquefied after passing through the condenser 13, releasing heat in the condenser 13. After absorbing heat in the evaporator 15, the refrigerant becomes gaseous and is output to the compressor 12. In the thermal management system for cooling the battery pack, the condenser 13 is used to heat the battery pack 52 in the vehicle or energy storage cabinet, and the evaporator 15 is used to cool the battery pack 52 in the vehicle or energy storage cabinet. It can be understood that the evaporator 15 is a liquid-cooled evaporator 151 or an air-cooled evaporator 152 (e.g., Figure 9 At least one of them.

[0093] The input terminals of bypass branch 20 and condenser 13 are both connected to the output terminal of compressor 12, and the output terminals of bypass branch 20 and condenser 13 are both connected to the input terminal of evaporator 15. That is, compressor 12 is used to supply refrigerant to bypass branch 20 and condenser 13 respectively, and evaporator 15 is used to receive refrigerant flowing from bypass branch 20 and condenser 13, and to supply refrigerant to compressor 12.

[0094] Specifically, in the thermal management system 1, the refrigerant output from the compressor 12 selectively enters at least one of the liquid-cooled evaporator 151 or the air-cooled evaporator 152 through at least one of the bypass branch 20 or the condenser 13. The output end of the compressor 12 is used to connect the input end of the bypass branch 20 and the input end of the condenser 13 respectively. The output end of the bypass branch 20 and the output end of the condenser 13 are used to supply refrigerant to the input end of at least one of the liquid-cooled evaporator 151 or the air-cooled evaporator 152. The thermal management system 1 is used to selectively connect 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.

[0095] In this embodiment, a portion of the high-temperature, high-pressure gaseous refrigerant flowing from the output of the compressor 12 flows out through the condenser 13, while the other portion flows out through the bypass branch 20. The refrigerant flowing out through the condenser 13 is at a lower temperature and contains a large amount of liquid refrigerant, while the refrigerant flowing out through the bypass branch 20 remains a high-temperature gaseous refrigerant since it has not passed through the condenser 13. By selectively connecting at least one of the input ends of the bypass branch and the input end of the condenser to the output end of the compressor, that is, both the low-temperature refrigerant flowing out through the condenser 13 and the high-temperature refrigerant flowing out through the bypass branch 20 flow to the evaporator 15, they can be effectively mixed in the evaporator 15. The high-temperature and low-temperature refrigerants exchange heat fully in the evaporator 15, effectively heating the refrigerant flowing into the evaporator 15 from the condenser 13. This effectively increases the superheat of the refrigerant at the outlet of the evaporator 15, ensuring that the refrigerant entering the compressor 12 has a certain suction superheat. This effectively reduces or eliminates the risk of liquid carryover during the suction of the compressor 12 in low-temperature environments, improving the operational reliability of the compressor 12. In addition, since the thermal management system 1 in this embodiment makes full use of the existing compressor 12, by adding a bypass branch 20, it can effectively improve the superheat of the compressor 12 in the low temperature environment, improve the operating reliability of the compressor 12, and also effectively save costs and improve competitiveness.

[0096] It is understood that the thermal management system 1 in this embodiment can operate normally not only in low-temperature environments but also in high-temperature environments. For example, in some embodiments, when the ambient temperature of the battery pack 52 is lower than a first threshold or the temperature of the battery pack 52 is lower than a 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, as well as the refrigerant input by the compressor 12 to the condenser 13 and 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 this embodiment, when the ambient temperature of the battery pack 52 is lower than the first threshold or the temperature of the battery pack 52 is lower than the second threshold, the bypass branch 20 connects the output end of the compressor 12 and the input end of the evaporator 15. This allows the high-temperature gaseous refrigerant output from the compressor 12 to be transported to the evaporator 15 via the bypass branch 20, where it mixes and heats with the low-temperature refrigerant supplied to the evaporator 15 from the condenser 13. This effectively solves the problem of liquid carryover during compressor suction in low-temperature environments, improving the operational reliability of the compressor 12. It is understood that when the ambient temperature is high, such as when the ambient temperature of the battery pack 52 is higher than the first threshold and the temperature of the battery pack 52 is higher than the second threshold, the bypass branch 20 can be disconnected, while still ensuring the operational stability of the compressor 12.

[0097] It should be noted that the ambient temperature of the battery pack 52 refers to the temperature of the cavity in which the battery pack 52 is housed. For example, this could be the atmospheric temperature inside the cabinet in an energy storage unit where the battery pack 52 is housed, or the atmospheric temperature inside a vehicle where the battery pack 52 is housed. This temperature can be monitored in real time using temperature sensors. The temperature of the battery pack 52 itself refers to the temperature collected by the temperature sensor installed inside the battery pack 52.

[0098] Reference Figure 1 For ease of description, the branch containing the compressor 12, condenser 13 and evaporator 15 is designated as the main branch 10, and the pipeline of the main branch 10 is designated as the first pipeline 11. The main branch 10 also includes a first expansion valve 14, which is connected between the output end of the condenser 13 and the input end of the evaporator 15.

[0099] Specifically, the compressor 12, condenser 13, first expansion valve 14, and evaporator 15 are connected in series via a first pipe 11. 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 connected to the output end of the evaporator 15 via the first pipe 11, and the output end of the compressor 12 is connected to the input end of the condenser 13 via the first pipe 11. Similarly, 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 connected to the output end of the condenser 13 via the first pipe 11, and the output end of the first expansion valve 14 is connected to the input end of the evaporator 15 via the first pipe 11.

[0100] The main circuit 10 is primarily used for the circulation of refrigerant. The first expansion valve 14 is used to throttle the liquid refrigerant into a low-temperature wet vapor state. It should be noted that the low-temperature wet vapor state of the refrigerant refers to its presence in a mist-like (or tiny droplet) form; at this stage, the refrigerant still contains some liquid components and has not completely converted into a gaseous state.

[0101] Specifically, gaseous refrigerant enters compressor 12 from its input end, is processed by compressor 12, and then outputs high-temperature, high-pressure gaseous refrigerant from its output end. This high-temperature, high-pressure gaseous refrigerant flows through the first pipe 11 to the input end of condenser 13, then enters condenser 13. While passing through condenser 13, it releases heat to achieve a heating effect. Liquid refrigerant then flows out from the output end of condenser 13. The liquid refrigerant then flows through the first pipe 11 to the input end of the first expansion valve 14. Under the action of the first expansion valve 14, low-temperature refrigerant flows out from its output end. This low-temperature refrigerant then flows through the first pipe 11 to the input end of evaporator 15, and then gaseous refrigerant flows out from the output end of evaporator 15. The gaseous refrigerant then flows through the first pipe 11 back to the input end of compressor 12, and this cycle repeats continuously.

[0102] In this embodiment, a portion of the high-temperature, high-pressure gaseous refrigerant flowing from the output of the compressor 12 passes sequentially through the condenser 13 and the first expansion valve 14, while the other portion flows out through the bypass branch 20. The refrigerant flowing through the condenser 13 and the first expansion valve 14 is low-temperature, while the refrigerant flowing through the bypass branch 20 remains high-temperature gaseous refrigerant as it does not pass through the condenser 13. Both the low-temperature refrigerant flowing through the condenser 13 and the first expansion valve 14, and the high-temperature refrigerant flowing through the bypass branch 20, flow towards the evaporator 15, allowing for effective mixing within the evaporator 15. This effectively heats the low-temperature refrigerant, increasing the refrigerant superheat at the outlet of the evaporator 15 and ensuring that the refrigerant entering the compressor 12 has a certain suction superheat. This effectively reduces or eliminates the risk of liquid carryover during compressor suction in low-temperature environments, improving the operational reliability of the compressor 12. In addition, since the thermal management system 1 in this embodiment makes full use of the existing compressor 12, there is no need to add additional equipment for heating the low-temperature refrigerant flowing out of the first expansion valve 14. By adding a bypass branch 20, the superheat of the compressor 12 can be effectively improved, the reliability of the compressor 12 can be improved, and costs can be effectively saved and competitiveness can be improved.

[0103] To effectively control the suction superheat of compressor 12, in some embodiments, the suction superheat of compressor 12 is controlled by controlling the flow rate of refrigerant flowing out of bypass branch 20. For example, the heating capacity of the low-temperature refrigerant flowing from condenser 13 to evaporator 15 can be improved by increasing the flow rate of high-temperature refrigerant flowing out of bypass branch 20. Alternatively, the flow rate of high-temperature refrigerant flowing out of bypass branch 20 can be reduced or shut off to adjust the suction superheat of compressor 12.

[0104] Reference Figure 1 In some embodiments, the bypass branch 20 includes a first throttle valve 22 disposed on the bypass branch 20. The first throttle valve 22 is used to open or close the bypass branch 20, or to regulate the flow rate of refrigerant input from the output terminal of the compressor 12 to the input terminal of the evaporator 15 through the bypass branch 20. For ease of description, the pipeline of the bypass branch 20 is designated as the second pipeline 21, and the first throttle valve 22 is connected in series on the second pipeline 21.

[0105] Reference Figure 1In some embodiments, the input end of the first throttle valve 22 is connected between the output end of the compressor 12 and the input end of the condenser 13 via a second pipe 21, and the output end of the first throttle valve 22 is connected between the input end of the evaporator 15 and the output end of the first expansion valve 14 via the second pipe 21. That is, part of the high-temperature, high-pressure gaseous refrigerant flowing out of the output end of the compressor 12 flows from the first pipe 11 to the condenser 13 and the first expansion valve 14, and another part flows from the second pipe to the first throttle valve 22. Low-temperature refrigerant flows out from the first expansion valve 14, and high-temperature gaseous refrigerant flows out from the first throttle valve 22. Then, both the low-temperature refrigerant flowing out from the first expansion valve 14 and the high-temperature gaseous refrigerant flowing out from the first throttle valve 22 flow to the evaporator 15 and mix there, so as to heat the low-temperature refrigerant with the high-temperature gaseous refrigerant. In this embodiment, since the first throttle valve 22 can control the flow rate of refrigerant through the second pipeline 21, the flow rate of refrigerant through the second pipeline 21 can be adjusted and controlled in different application scenarios to achieve the ratio of low-temperature refrigerant flowing out of the first expansion valve 14 to high-temperature gaseous refrigerant flowing out of the first throttle valve 22. This controls the suction superheat of the compressor 12, reduces the risk of liquid carryover in the suction, and improves the operational reliability of the compressor 12. The thermal management system 1 in this embodiment can adapt to more application scenarios.

[0106] In some implementations, the first throttle valve 22 may be an expansion valve, which has the function of throttling and reducing pressure.

[0107] In order to achieve dynamic adjustment and control of the suction superheat of compressor 12 and improve the environmental adaptability of thermal management system 1, refer to Figure 1 In some embodiments, the thermal management system 1 further includes 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 to the compressor 12. The controller 32 is used to control the first throttle valve 22 to regulate the flow rate of the refrigerant input from the output of the compressor 12 to the input of the evaporator 15 through the bypass branch 20 based on the temperature and pressure of the refrigerant input to the compressor 12 detected by the sensor 31. That is, after the sensor 31 detects the temperature and pressure of the refrigerant input to the compressor 12, it transmits the detected temperature and pressure values ​​to the controller 32. The controller 32 can receive the detection information from the sensor 31 and perform corresponding control based on the received detection information from the sensor 31.

[0108] In some implementations, the sensor is a temperature and pressure sensor.

[0109] 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. Then, the controller 32 controls the flow rate of the first throttle 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 liquid carryover in the suction, and improve the operational reliability of the compressor 12.

[0110] It is understood that in some other embodiments, a humidity sensor can be used instead of the sensor 31 mentioned above. The humidity sensor detects the humidity of the refrigerant entering the compressor 12, and the controller 32 determines the proportion of liquid refrigerant entering the compressor 12 based on the humidity detected by the humidity sensor. Then, the first throttle valve 22 is controlled to adjust the flow rate accordingly, which can also reduce the risk of liquid carryover during suction and improve the operational reliability of the compressor 12.

[0111] In some embodiments, the controller 32 is used to control the first throttle valve 22 to regulate the flow rate of refrigerant input from the output of the compressor 12 to the input of the evaporator 15 via the bypass branch 20, based on at least one of the temperature and pressure of the refrigerant input to 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, the flow rate of the first throttle valve 22 can be controlled not only by monitoring at least one of the temperature or pressure of the refrigerant input to the compressor 12, but also by monitoring at least one of the ambient temperature of the battery pack 52 or the temperature of the battery pack 52, thereby improving fault tolerance.

[0112] Reference Figure 1 In some embodiments, the thermal management system 1 further includes a second throttle valve 16, which is disposed on a pipeline connecting the output end of the compressor 12 and the input end of the condenser 13. The second throttle valve 16 is used to control the flow rate of refrigerant from the compressor 12 to the condenser 13.

[0113] Specifically, the second throttle valve 16 is connected in series between the output end of the compressor 12 and the input end of the condenser 13 via 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 throttle valve 16. In this embodiment, the flow rate of the high-temperature gaseous refrigerant flowing from the output end of the compressor 12 to the condenser 13 can be controlled by controlling the flow rate of the second throttle valve 16. Similarly, the ratio of the low-temperature refrigerant flowing out from the output end of the first expansion valve 14 to the high-temperature gaseous refrigerant flowing out from the output end of the bypass branch 20 can be controlled to ensure that the refrigerant entering the compressor 12 has a certain suction superheat, thereby reducing the risk of liquid carryover during suction and improving the operational reliability of the compressor 12.

[0114] In some implementations, the second throttle valve 16 may be an expansion valve, which has the function of throttling and reducing pressure.

[0115] Reference Figure 1 The thermal management system 1 also includes a radiator 42. It is understood that the radiator 42 is typically exposed to the external environment; for example, the radiator 42 in the energy storage cabinet is exposed to the air outside the energy storage cabinet, and the radiator 42 in the vehicle is exposed to the air outside the passenger compartment, to exchange heat with the outside air. Through the arrangement of the radiator 42, the thermal management system 1 in this embodiment can heat or dissipate heat to the energy storage cabinet or the vehicle's battery pack 52 in various ways. Specifically, heating or dissipating heat can be targeted according to the ambient temperature of the battery pack 52 or the temperature of the battery pack 52.

[0116] Reference Figure 1 For example, in some embodiments, when the ambient temperature of the battery pack 52 is T1, or when the temperature of the battery pack 52 is T2, the condenser 13 is connected to the liquid cooling plate of the battery pack 52 to heat the battery pack 52, and the bypass branch 20 connects 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, as well as the refrigerant input by the compressor 12 to the condenser 13 and output by the condenser 13. When the ambient temperature of the battery pack 52 is T3, or the temperature of the battery pack 52 is T4, the radiator 42 is connected to the liquid cooling plate of the battery pack 52 to dissipate heat from the battery pack 52; when the ambient temperature of the battery pack 52 is T5, or the temperature of the battery pack 52 is T6, the evaporator 15 is connected to the liquid cooling plate of the battery pack 52 to dissipate heat from the battery pack 52. At this time, the input end of the evaporator 15 receives the refrigerant output from the condenser 13, and the evaporator 15 is connected to the liquid cooling plate of the battery pack 52 to cool the battery pack 52; wherein, T1 < first threshold < T3 < T5, T2 < second threshold < T4 < T6.

[0117] It is understood that T1-T6 represents a range of values, not a single 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 and the temperature of T2 is less than the second threshold, at this temperature environment, a portion of the high-temperature gaseous refrigerant flowing out of the compressor 12 flows to the condenser 13 for heat exchange with the liquid in the liquid cooling plate of the battery pack 52 through the condenser 13, and also heats the battery pack 52. The other portion of the high-temperature gaseous refrigerant flowing out of the compressor 12 flows to the evaporator 15 through the bypass branch 20, mixing and heating the refrigerant flowing from the condenser 13 to the evaporator 15. This effectively reduces the risk of liquid carryover in the compressor 12's suction gas at low temperatures, improving the operational stability of the compressor 12. When the ambient temperature of the battery pack 52 is T3 and the temperature of the battery pack 52 is T4, where T3 is greater than the first threshold and T4 is greater than the second threshold, the ambient temperature will not drop to the point where the compressor 12 cannot operate stably. Therefore, the bypass branch 20 is disconnected, for example, by reducing the flow rate of the first throttle valve 22 to 0. At this point, the radiator 42 can be connected to the liquid cooling plate of the battery pack 52, dissipating heat through the radiator 42 without requiring the compressor 12 to cool the battery pack 52, effectively reducing the energy consumption of the compressor 12. However, when the temperature rises further, for example, when the ambient temperature of the battery pack 52 is T5 or the temperature of the battery pack 52 is T6, the compressor 12 needs to operate. The evaporator 15 is connected to the liquid cooling plate of the battery pack 52 to dissipate heat. Because the temperature is high enough, the proportion of liquid refrigerant in the refrigerant flowing from the evaporator 15 will not be too high. Therefore, it is not necessary to use the bypass branch 20 to direct a portion of the high-temperature refrigerant flowing from the compressor 12 to the evaporator 15.

[0118] Reference Figure 1In some embodiments, the condenser 13 includes a liquid-cooled condenser 131, which is used for heat exchange between the refrigerant flowing through the liquid-cooled condenser 131 and other liquids flowing through the liquid-cooled condenser 131. The liquid-cooled condenser 131 includes a first input terminal and a first output terminal connected together, as well as a second input terminal and a second output terminal connected together. It can be understood that the first input terminal and the first output terminal of the liquid-cooled condenser 131 are equivalent to the inlet and outlet on the refrigerant side of the liquid-cooled condenser 131, and the second input terminal and the second output terminal of the liquid-cooled condenser 131 are equivalent to the inlet and outlet on the water-cooled side of the liquid-cooled condenser 131. Evaporator 15 includes a liquid-cooled evaporator 151, which is used for heat exchange between the refrigerant flowing through it and other liquids flowing through it. The liquid-cooled evaporator 151 includes a first input terminal and a first output terminal connected together, as well as a second input terminal and a second output terminal connected together. It can be understood that the first input terminal and the first output terminal of the liquid-cooled evaporator 151 correspond to the inlet and outlet on the refrigerant side of the liquid-cooled evaporator 151, and the second input terminal and the second output terminal correspond to the inlet and outlet on the water-cooled side of the liquid-cooled evaporator 151. The input terminal of bypass branch 20 and the first input terminal of condenser 13 are both connected to the output terminal of compressor 12, and the output terminal of bypass branch 20 and the first output terminal of condenser 13 are both connected to the first input terminal of evaporator 15.

[0119] It is understandable that the thermal management system 1 can autonomously control the heating and cooling of the battery pack 52. To achieve effective control of the heating or cooling of the battery pack 52 by the thermal management system 1, refer to... Figure 1 The thermal management system 1 also includes a multi-way valve 80 and a controller 32. The multi-way valve 80 includes an interface for connecting to the liquid cooling plate of the battery pack 52, an interface for connecting to the radiator 42, an interface for connecting to the second input and second output of the condenser 13, and an interface for connecting to the second input and second output of the evaporator 15. The controller 32 is used to control the connection mode between the interfaces of the multi-way valve 80.

[0120] For example, in some implementations, when the ambient temperature of the battery pack 52 is T1, or the temperature of the battery pack 52 is T2, the controller 32 controls the interfaces of the multi-way valve 80 connected to the condenser 13 and the multi-way valve 80 connected to the liquid cooling plate of the battery pack 52, and the bypass branch 20 connects the output end of the compressor 12 and the input end of the evaporator 15, for example, by controlling the flow rate of the first throttle valve 22 to be greater than 0 through the controller 32. When the ambient temperature of the battery pack 52 is T3, or the temperature of the battery pack 52 is T4, the controller 32 controls the interfaces of the multi-way valve 80 connected to the radiator 42 and the multi-way valve 80 connected to the liquid cooling plate of the battery pack 52; when the ambient temperature of the battery pack 52 is T5, or the temperature of the battery pack 52 is T6, the controller 32 controls the interfaces of the multi-way valve 80 connected to the evaporator 15 and the multi-way valve 80 connected to the liquid cooling plate of the battery pack 52. In this embodiment, by controlling the multi-way valve 80 through the controller 32, the heating or cooling method of the thermal management system 1 for 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 operating temperature, thereby improving the performance of the battery pack 52.

[0121] Understandably, in order to improve the heat exchange efficiency between the liquid in the liquid-cooled plate of the battery pack 52 and the condenser 13 or evaporator 15, the thermal management system 1 also includes a first pump 62 and a second pump 72. The first pump 62 and the second pump 72 are used to accelerate the flow rate of the liquid flowing through the liquid-cooled plate of the battery pack 52 in different modes. The first pump 62 and the second pump 72 are both connected to the interface of the multi-way valve 80, so as to control the connection between the first pump 62 or the second pump 72 and the liquid-cooled plate of the battery pack 52 through the control valve.

[0122] Reference Figure 1 For ease of description, the branch containing radiator 42 is designated as heat dissipation branch 40, and the pipe of heat dissipation branch 40 is designated as third pipe 41. Radiator 42 is mounted on third pipe 41. The branch containing battery pack 52 is designated as heat source branch 50, and the pipe of heat source branch 50 is designated as fourth pipe 51. Battery pack 52 is a heat source connected in series with fourth pipe 51. The branch containing first pump 62 is designated as first branch 60, and the pipe of first pump branch 60 is designated as fifth pipe 61. First pump 62 is connected in series with fifth pipe 61. The branch containing second pump 72 is designated as second pump branch 70, and the pipe of second pump branch 70 is designated as sixth pipe 71. Second pump 72 is connected in series with sixth pipe 71.

[0123] 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 mode switching of the thermal management system 1 through the multi-way valve 80.

[0124] It is understood that the number of multi-way valves 80 can be one or more. 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 respectively 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, so as to realize the 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.

[0125] It should be noted that each port of the multi-way valve 80 in the attached diagram is marked with a number. The first port corresponds to number 1 in the attached diagram, the second port corresponds to number 2, the third port corresponds to number 3, the fourth port corresponds to number 4, the fifth port corresponds to number 5, the sixth port corresponds to number 6, the seventh port corresponds to number 7, and the eighth port corresponds to number 8.

[0126] Specifically, refer to Figure 1 The input and output ends of the heat dissipation branch 40 are connected to the two ports of the multi-way valve 80. For example, the input end of the radiator 42 can be connected to the fourth port through the third pipe 41, and the output end of the radiator 42 can be connected to the first port through the third pipe 41.

[0127] The input and output ends of the heat source branch 50 are connected to the other two ports of the multi-way valve 80, respectively. For example, the input end of the battery pack 52 can be connected to the second port through the fourth pipe 51, and the output end of the battery pack 52 can be connected to the seventh port through the fourth pipe 51. It can be understood that the battery pack 52 is connected to the second and fourth ports of the multi-way valve 80 through its liquid cooling plate via the fourth pipe 51.

[0128] The first input terminal of the liquid-cooled condenser 131 is connected to the output terminal of the compressor 12 through the first pipe 11, and the first output terminal of the liquid-cooled condenser 131 is connected to the first expansion valve 14 through the first pipe 11. It should be noted that the liquid-cooled condenser 131 is a liquid-to-liquid heat exchanger, such as a refrigerant-to-water heat exchanger.

[0129] The fifth pipe 61 is connected to the second input and second output terminals of the liquid-cooled condenser 131, respectively, to connect the condenser 131 and the first pump 62 in series. The input and output terminals of the first pump branch 60 are connected to two more ports of the multi-way valve 80. For example, the output terminal of the first pump 62 can be connected to the second input terminal of the liquid-cooled condenser 131 through the fifth pipe 61, the input terminal of the first pump 62 can be connected to the sixth port through the fifth pipe 61, and the second output terminal of the liquid-cooled condenser 131 can be connected to the fifth port through the fifth pipe 61. It can be understood that the first pump 62 can be a water pump.

[0130] The first input terminal of the liquid-cooled evaporator 151 is connected to the output terminal of the first expansion valve 14 via the first pipe 11, and the first output terminal of the liquid-cooled evaporator 151 is connected to the input terminal of the compressor 12 via the first pipe 11. It should be noted that the liquid-cooled evaporator 151 involves heat exchange between liquids, such as heat exchange between refrigerant and water.

[0131] The sixth pipe 71 is connected to the second input and second output terminals of the liquid-cooled evaporator 15, and connects the first pump 62 and the evaporator 15 in series. The input and output terminals of the second pump branch 70 are connected to the two ports of the multi-way valve 80. For example, the output terminal of the second pump 72 can be connected to the second input terminal of the liquid-cooled evaporator 151 through the sixth pipe 71, the input terminal of the second pump 72 can be connected to the eighth port through the sixth pipe 71, and the second output terminal of the liquid-cooled evaporator 151 can be connected to the third port. It can be understood that the second pump 72 can be a water pump.

[0132] By changing the connection method of the eight ports of the multi-way valve 80, the thermal management system 1 in this embodiment can switch to different modes to cope with different working scenarios.

[0133] Figure 2 for Figure 1 One of the schematic diagrams of the heating battery pack 52 of the thermal management system 1 in the embodiment.

[0134] Reference Figure 2 The thermal management system 1 includes a mode for heating the battery pack 52. This mode is mainly used in scenarios with low ambient temperatures, such as when the ambient temperature of the battery pack 52 is below a first threshold or the temperature of the battery pack 52 is below a second threshold. In this mode, a bypass branch connects the output of the compressor 12 to the input of the liquid-cooled evaporator 151, and the liquid-cooled condenser 131 is connected to the liquid cooling plate of the battery pack 52 to heat the battery pack 52.

[0135] Specifically, the first and eighth ports of the multi-way valve 80 are connected, the second and fifth ports are connected, the third and fourth ports are connected, and the sixth and seventh ports are connected.

[0136] 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) flowing out from the output end of the battery pack 52 flows to the input end of the first pump 62 through the seventh and sixth interfaces, 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 through the second output end of the liquid-cooled condenser 131 to the fifth and second interfaces, and finally flows to the input end of the battery pack 52, thus repeating the cycle. During the cycle, 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, thereby increasing the temperature of the liquid when it flows to the battery pack 52, and thus heating the battery pack 52.

[0137] Meanwhile, the second pump branch 70 and the heat dissipation branch 40 are connected via a multi-way valve 80. Specifically, the first and eighth ports are connected, and the third and fourth ports are connected. Liquid (such as water) output from the radiator 42 flows through the first and eighth ports to the second pump 72, then through the second pump 72 to the second input end of the liquid-cooled evaporator 151, and through the second output end of the liquid-cooled evaporator 151 to the third and fourth ports, finally flowing back to the radiator 42, thus repeating the cycle. During the liquid circulation process, when passing through the liquid-cooled evaporator 151, it exchanges heat with the low-temperature refrigerant inside the liquid-cooled evaporator 151, lowering the temperature of the liquid flowing from the liquid-cooled evaporator 151 to the radiator 42. The cooled liquid, when flowing through the radiator 42, can exchange heat with the outside air, absorbing heat from the outside air. In this process, the heat from the outside air is used to heat the low-temperature refrigerant, causing the refrigerant to vaporize.

[0138] In this mode, the high-temperature, high-pressure gaseous refrigerant flowing from the output of compressor 12 is partially cooled by the liquid-cooled condenser 131 to heat the battery pack 52, and then forms low-temperature refrigerant through the first expansion valve 14. The remaining portion flows directly to the liquid-cooled evaporator 151 as high-temperature gaseous refrigerant through the first throttling valve 22, where it mixes with the low-temperature refrigerant to heat it. In this mode, the low-temperature refrigerant, when passing through the liquid-cooled evaporator 151, not only absorbs heat from the external environment but is also heated by the high-temperature gaseous refrigerant flowing from the bypass branch 20. This ensures that even at low ambient temperatures, it is still sufficiently heated to become gaseous refrigerant, thus controlling the suction superheat of compressor 12 within the normal range, reducing the risk of liquid carryover during compressor suction, and improving the operational reliability of compressor 12.

[0139] Figure 3 for Figure 1 Another schematic diagram of the heating battery pack 52 mode of the thermal management system 1 in the embodiment.

[0140] Reference Figure 3 , Figure 3 The mode of the heated battery pack 52 in the embodiment is the same as Figure 2 The main difference is that the third interface and the eighth interface are connected, and the first interface and the fourth interface are connected. In this embodiment, the liquid-cooled evaporator 151 is no longer connected to the radiator 42, that is, the refrigerant flowing through the liquid-cooled evaporator 151 can no longer absorb heat from the outside air. At this time, part of the high-temperature and high-pressure gaseous refrigerant flowing out from the output end of the compressor 12 heats and cools the battery pack 52 through the liquid-cooled condenser 131, and then forms low-temperature refrigerant through the first expansion valve 14. The other part flows directly 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.

[0141] In this embodiment, the low-temperature refrigerant flowing out of the first expansion valve 14 can no longer absorb heat from the outside air; 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 to extremely low-temperature environments, such as application scenarios where the ambient temperature is below the boiling point of the refrigerant.

[0142] Figure 4 for Figure 1 A schematic diagram of the heat pump mode heating battery pack 52 of the thermal management system 1 in the embodiment.

[0143] Reference Figure 4 In some embodiments, the thermal management system 1 also includes an air-source heat pump mode for heating the battery pack 52. In this embodiment, the heat pump mode is mainly applied when the ambient temperature of the battery pack 52 is greater than a first threshold and the temperature of the battery pack 52 is greater than a second threshold. At this time, the bypass branch 20 is disconnected, and the output end of the compressor 12 is not connected to the input end of the liquid-cooled evaporator 151. The liquid-cooled condenser 131 is connected to the liquid-cooled plate of the battery pack 52 to heat the battery pack 52. This embodiment, compared to... Figure 2 The main difference in the embodiment is that the hot gas bypass branch 20 is disconnected, that is, 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 flows to the liquid-cooled condenser 131, and then flows to the liquid-cooled evaporator 151 through the first expansion valve 14. It exchanges heat with the liquid (such as water) flowing through the liquid-cooled evaporator 151. The heat of the liquid flowing through the liquid-cooled evaporator 151 is absorbed from the air in the external environment through the radiator 42. That is, most of the heat absorbed by the low-temperature refrigerant flowing out of the first expansion valve 14 when passing through the liquid-cooled evaporator 151 comes from the air in the external environment.

[0144] In this embodiment, the ambient temperature used in the heat pump mode is higher than that of the environment. Figure 2 The ambient temperature at which the example was applied.

[0145] Figure 5 for Figure 1 A schematic diagram of the natural heat dissipation mode of the thermal management system 1 in the embodiment for cooling the battery pack 52.

[0146] Reference Figure 5 In some embodiments, the thermal management system 1 includes a natural heat dissipation mode for cooling the battery pack 52. In this embodiment, the natural heat dissipation mode is primarily used when both the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are relatively low. Figure 4 In the embodiment where the temperature is higher, the battery pack requires heat dissipation. In this mode, the bypass branch 20 is disconnected, and the output of the compressor 12 is not connected to the input of the liquid-cooled evaporator 151. The radiator 42 is connected to the liquid cooling plate of the battery pack 52 to dissipate heat for the battery pack 52.

[0147] Specifically, in natural cooling mode, the first and eighth ports of the multi-way valve 80 are connected, as are the second and third ports, the fourth and fifth ports, and the sixth and seventh ports. In this mode, the first throttle valve 22 and the second throttle valve 16 are disconnected, and the compressor 12 does not operate.

[0148] 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 via a multi-way valve 80. The liquid (such as water) flowing out from the output end of the battery pack 52 flows through the seventh and sixth interfaces to the input end of the first pump 62, then from the output end of the first pump 62 to the second input end of the liquid-cooled condenser 131, and then through the second output end of the liquid-cooled condenser 131 to the fifth and fourth interfaces, and then to the output end of the radiator 42. It then flows out from the output end of the radiator 42, and then sequentially through the first and eighth interfaces to the input end of the second pump 72, then through the output end of the second pump 72 to the second input end of the liquid-cooled evaporator 151, and then through the second output end of the liquid-cooled evaporator 151 to the third and second interfaces, and finally to the input end of the battery pack 52, and so on in a continuous cycle. In this mode, the liquid flowing through the battery pack 52 exchanges heat with the heat emitted by the battery pack 52, raising the temperature of the liquid flowing out of the battery pack 52. Then, as it flows through the radiator 42, it exchanges heat with the air in the external environment, lowering the temperature of the liquid after passing through the radiator 42, thus 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. Therefore, in this mode, the battery pack 52 can be cooled naturally by the radiator 42. Because the compressor 12 does not work, energy consumption can be effectively reduced.

[0149] It is understood that the ambient temperature in which the natural heat dissipation mode in this embodiment is applied is typically high, and higher than [the ambient temperature]. Figure 4 The ambient temperature at which the heat pump mode is applied in the embodiment.

[0150] Figure 6 for Figure 1 A schematic diagram of the compressor 12 of the thermal management system 1 in the embodiment cooling the battery pack 52 in cooling mode.

[0151] Reference Figure 6 In some embodiments, the thermal management system 1 includes a compressor 12 cooling mode for cooling the battery pack 52. In this embodiment, the compressor 12 cooling mode is primarily used when both the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are relatively low. Figure 5 In the embodiment where the temperature is higher, the battery pack still needs heat dissipation. In this mode, the bypass branch 20 is disconnected, and the output terminal of the compressor 12 is not connected to the input terminal of the liquid-cooled evaporator 151. The liquid-cooled evaporator 151 is connected to the liquid cooling plate of the battery pack 52 for cooling the battery pack 52.

[0152] Specifically, in the refrigeration mode of compressor 12, the first and sixth ports of multi-way valve 80 are connected, the second and third ports are connected, the fourth and fifth ports are connected, and the seventh and eighth ports are connected. Additionally, in this mode, the first throttle valve 22 is disconnected to disconnect the bypass branch 20.

[0153] In this mode, the compressor 12 operates normally, the liquid-cooled evaporator 151 can achieve the cooling function, and the liquid-cooled condenser 131 can achieve the heating function.

[0154] The heat source branch 50 and the second pump branch 70 are connected by a multi-way valve 80. Liquid (such as water) flowing from the output end of the battery pack 52 flows through the seventh and eighth ports to the input end of the second pump 72, then from the output end of the second pump 72 to the second input end of the liquid-cooled evaporator 151, and then through the second output end of the liquid-cooled condenser 131 to the third and second ports, and finally to the input end of the battery pack 52, thus repeating the cycle. During the cycle, the low-temperature refrigerant flowing from the output end of the first expansion valve 14 to the liquid-cooled evaporator 151 exchanges heat with the liquid flowing from the second water pump to the liquid-cooled evaporator 151, thereby lowering the temperature of the liquid when it flows out of the liquid-cooled evaporator 151. The low-temperature liquid can cool the battery pack 52 when it flows through it.

[0155] Meanwhile, the heat dissipation branch 40 and the first pump branch 60 are connected by a multi-way valve 80. The liquid (such as water) output from the radiator 42 flows through the first port and the sixth port to the first pump 62, then through the first pump 62 to the second input end of the liquid-cooled condenser 131, and through the second output end of the liquid-cooled condenser 131 to the fifth port and the fourth port, and finally back to the radiator 42, thus repeating the cycle. During the liquid circulation process, when passing through the liquid-cooled condenser 131, it exchanges heat with the high-temperature gaseous refrigerant inside the liquid-cooled condenser 131, raising the temperature of the liquid flowing from the liquid-cooled condenser 131 to the radiator 42. The heated liquid then exchanges heat with the outside air as it flows through the radiator 42, dissipating the heat into the outside air. This repeated cycle achieves the cooling of the battery pack 52.

[0156] It is understood that the ambient temperature in which the compressor 12 cooling mode is applied in this embodiment is typically high, and usually higher than [temperature value missing]. Figure 5 The ambient temperature used in the natural heat dissipation mode described in this embodiment.

[0157] Figure 7 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0158] Reference Figure 7 Bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 can be referenced. Figure 1 The bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 in this embodiment will not be described again here. The thermal management system 1 in this embodiment and Figure 1 The main difference in the thermal management system 1 in this embodiment is that the main circuit 10 in this embodiment does not have a second throttle valve 16, while the other structures of the main circuit 10 are the same. In this embodiment, since the second throttle valve 16 is not provided, the proportion of refrigerant flowing from 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 to effectively control the suction superheat of the compressor 12.

[0159] It is understood that the thermal management system 1 in this embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same, and will not be described again here.

[0160] Figure 8This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0161] Reference Figure 8 Bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 can be referenced. Figure 1 The bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 in this embodiment will not be described again here. The thermal management system 1 in this embodiment and Figure 1 The main difference in the thermal management system 1 in this embodiment is that a multi-way throttle valve 90 is used instead of a multi-way throttle valve 90. Figure 1 The first throttle valve 22 and the second throttle valve 16 in the embodiment.

[0162] Specifically, the thermal management system 1 also includes a multi-way throttle valve 90, such as a three-way throttle valve 90a. The multi-way throttle valve 90 includes a first interface 91, a second interface 92, and a third interface 93. The first interface 91 is connected to the output end of the compressor 12 through a first pipe 11, the second interface 92 is connected to the input end of the condenser 13 through the first pipe 11, and the third interface 93 is connected to the input end of the bypass branch 20. In this embodiment, using a three-way throttle valve 90a instead of the first throttle valve 22 and the second throttle valve 16 can reduce the number of valves, thereby simplifying the control system, reducing the failure rate, and potentially reducing the overall cost.

[0163] It is understood that the multi-port throttle valve 90 in this embodiment has a throttling function, which can control the flow rate through the first port 91, the second port 92, and the third port 93. In some embodiments, the multi-port throttle valve 90 can be a multi-port expansion valve, which has a throttling and pressure-reducing function.

[0164] Figure 9 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0165] Reference Figure 9 Bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 can be referenced. Figure 1 The bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 in this embodiment will not be described again here. The thermal management system 1 in this embodiment and Figure 1 The main difference in the thermal management system 1 in the embodiment is the different structure of the main road 10.

[0166] Reference Figure 9In some embodiments, there are multiple evaporators 15, including air-cooled evaporators 152 and liquid-cooled evaporators 151. The air-cooled evaporator 152 is used to exchange heat between the refrigerant flowing through it and the gas outside it. For example, it can be used to cool the interior of the energy storage cabinet or to cool the passenger compartment of a vehicle. The liquid-cooled evaporator 151 is used to exchange heat between the refrigerant flowing through it and other liquids flowing through it. For example, it can be used to cool the battery pack 52 inside the energy storage cabinet or the vehicle's battery pack 52. In this embodiment, the output of the bypass branch 20 is connected to both the input of the air-cooled evaporator 152 and the output of the first expansion valve 14.

[0167] Reference Figure 9 In some embodiments, the thermal management system 1 further includes a second expansion valve 17 connected to the pipeline between the first input end of the liquid-cooled evaporator 151 and the output end of the condenser. The branch containing the air-cooled evaporator 152 and the first expansion valve 14 is connected in parallel with the branch containing the liquid-cooled evaporator 151 and the second expansion valve 17. In this case, 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 sequentially through the first expansion valve 14 and the air-cooled evaporator 152, or sequentially through the second expansion valve 17 and the liquid-cooled evaporator 151, or it can be divided into two parts flowing to the first expansion valve 14 and the second expansion valve 17 respectively. In this embodiment, since the main circuit 10 includes a liquid-cooled evaporator 151 and an air-cooled evaporator 152, it can not only cool the battery pack 52 of the heat source branch 50 through the liquid-cooled evaporator 151, but also cool the inner cavity of the energy storage cabinet or the passenger compartment of the vehicle through the air-cooled evaporator 152, thereby improving the functional diversity of the thermal management system 1 in this embodiment.

[0168] The second pump branch 70 is connected to the liquid-cooled evaporator 151, and the specific connection method is the same. Figure 1 The connection method between the second pump branch 70 and the liquid-cooled evaporator 151 in the embodiment is the same, and will not be described again here.

[0169] Reference Figure 9 In some embodiments, the fifth pipeline 61 is connected to the second input terminal and the outlet terminal of the liquid-cooled condenser 131, and the liquid-cooled condenser 131, the first pump 62 and the power module 63 are connected in series.

[0170] Reference Figure 9In some embodiments, the first pump branch 60 further includes a power module 63 connected in series with the fifth pipeline 61. The power module 63 is connected between the first pump 62 and the liquid-cooled condenser 131, meaning that the liquid flowing out of the first pump 62 passes through the power module 63 and then through the liquid-cooled condenser 131. Since the power module 63 is connected between the first pump 62 and the liquid-cooled condenser 131, the heat source branch 50 and the first pump branch 60 are connected. When the liquid-cooled condenser 131 heats the battery pack 52 of the heat source branch 50, the liquid flowing to the power module 63 is cooled after passing through the battery pack 52, thus reducing the impact of the liquid-cooled condenser 131 on the heating of the power module 63. This embodiment is mainly applied to scenarios where the battery pack 52 needs to be heated, but the power module 63 does not.

[0171] Understandable, Figure 9 The thermal management system 1 in the embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same.

[0172] Figure 9A for Figure 9 A schematic diagram of the heating battery pack 52 of the thermal management system 1 in the embodiment.

[0173] Reference Figure 9A In this embodiment, the compressor 12 cooling mode is mainly used in scenarios with low ambient temperatures, such as when the ambient temperature of the battery pack 52 is less than a first threshold or the temperature of the battery pack 52 is less than a second threshold. In this mode, the bypass branch 20 connects the output end of the compressor 12 to the input end of the air-cooled evaporator 152, and the liquid-cooled condenser 131 is connected to the liquid cooling plate of the battery pack 52 to heat the battery pack 52.

[0174] Specifically, in the heated battery pack 52 mode of this embodiment, the second interface and the fifth interface are connected, and the sixth interface and the seventh interface are connected, thereby connecting the first pump branch 60 and the heat source branch 50 through the multi-way valve 80. The branch where the second expansion valve 17 and the liquid-cooled evaporator 151 are located is disconnected, that is, the second expansion valve 17 is disconnected, and the refrigerant flowing from the condenser 13 will not flow through the second expansion valve 17 and the liquid-cooled evaporator 151. Moreover, 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, in the heated battery pack 52 mode, the air-cooled evaporator 152 cannot absorb heat from the external environment through the radiator 42. Thus, in this embodiment, the connection method between the first interface, the fourth interface, the third interface, and the eighth interface can be the same as... Figure 2 The implementation method is the same as that in 3 embodiments.

[0175] Taking the heated battery pack 52 in this embodiment as an example, when applied in an energy storage cabinet, it not only... Figure 2 or Figure 3 The same embodiment can heat the battery pack 52, and can also absorb heat from the inner cavity of the energy storage cabinet through the air-cooled evaporator 152 to cool and dehumidify the inner cavity of the energy storage cabinet.

[0176] Figure 9B for Figure 9 A schematic diagram of the heat pump mode heating battery pack 52 of the thermal management system 1 in the embodiment.

[0177] Reference Figure 9B In this embodiment, the heat pump mode is mainly applied when the ambient temperature of the battery pack 52 is greater than a first threshold and the temperature of the battery pack 52 is greater than a second threshold. At this time, the bypass branch 20 is disconnected, and the output terminal of the compressor 12 is not connected to the input terminal of the air-cooled evaporator 152. The liquid-cooled condenser 131 is connected to the liquid-cooled plate of the battery pack 52 to heat the battery pack 52. In this embodiment, the heat pump mode... Figure 4 As in this embodiment, the first throttle valve 22 needs to be disconnected to disconnect the bypass branch 20. The first expansion valve 14 can also be disconnected to disconnect the branch containing the first expansion valve 14 and the air-cooled evaporator 152. The working principle of the heat pump mode and its connection method with the multi-way valve 80 in this embodiment are the same. Figure 4 The basic principles are the same as in the embodiments, and can be referred to. Figure 4 Examples are not described in detail here.

[0178] It can be understood that in the heat pump mode of this embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened simultaneously so that the branch where the first expansion valve 14 and the air-cooled evaporator 152 are located are also connected.

[0179] Figure 9C for Figure 9A schematic diagram of the natural heat dissipation mode of the thermal management system 1 in the embodiment for cooling the battery pack 52.

[0180] Reference Figure 9C In this embodiment, the natural heat dissipation mode is mainly applied when both the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are lower than the ambient temperature. Figure 9B In the embodiment where the temperature is higher, the battery pack 52 requires heat dissipation. In this mode, the bypass branch 20 is disconnected, and the output of the compressor 12 is not connected to the input of the air-cooled evaporator 152. The radiator 42 is connected to the liquid cooling plate of the battery pack 52 to dissipate heat for the battery pack 52. In the natural heat dissipation mode of 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 simultaneously, and the compressor 12 does not work. The working principle of the natural heat dissipation mode in this embodiment and the connection method with the multi-way valve 80 are the same. Figure 5 The basic principles are the same as in the embodiments, and can be referred to. Figure 5 Examples are not described in detail here.

[0181] Figure 9D for Figure 9 A schematic diagram of the compressor 12 of the thermal management system 1 in the embodiment cooling the battery pack 52 in cooling mode.

[0182] Reference Figure 9D In this embodiment, the compressor 12 cooling mode is mainly applied when both the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are higher than the ambient temperature. Figure 9C In the embodiment where the temperature is higher, the battery pack 52 also requires heat dissipation. In this mode, the bypass branch 20 is disconnected, and the output of the compressor 12 is not connected to the input of the air-cooled evaporator 152. The liquid-cooled evaporator 151 is connected to the liquid cooling plate of the battery pack 52 to cool and dissipate heat for the battery pack 52. In the heat pump mode of this embodiment, the same Figure 6 As in this embodiment, the first throttle valve 22 needs to be disconnected to disconnect the bypass branch 20. The first expansion valve 14 can also be disconnected to disconnect the branch containing the first expansion valve 14 and the air-cooled evaporator 152. The working principle of the compressor 12 in cooling mode and its connection method with the multi-way valve 80 in this embodiment are the same. Figure 6 The basic principles are the same as in the embodiments, and can be referred to. Figure 6 Examples are not described in detail here.

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

[0184] Figure 10 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0185] Reference Figure 10 In some embodiments, the bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 may refer to Figure 1 The bypass branch 20, heat dissipation branch 40, heat source branch 50, first pump branch 60, and second pump branch 70 in this embodiment will not be described again here. The thermal management system 1 in this embodiment and Figure 9 The main difference in the thermal management system 1 in the embodiment is the different structure of the main road 10.

[0186] Specifically, the first expansion valve 14 and the liquid-cooled evaporator 151 are connected in series via the first pipe 11, and the second expansion valve 17 and the air-cooled evaporator 152 are connected in series via the first pipe 11. The branch containing the first expansion valve 14 and the liquid-cooled evaporator 151 and the branch containing the second expansion valve 17 and the air-cooled evaporator 152 are connected in parallel. The output of the bypass branch 20 is connected to the output of the first expansion valve 14 and the input of the liquid-cooled evaporator 151.

[0187] Understandable, Figure 10 The thermal management system 1 in the embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same.

[0188] Figure 10A for Figure 10 A schematic diagram of the heating battery pack 52 of the thermal management system 1 in the embodiment.

[0189] Compared to Figure 2 and Figure 3 The configuration of the heated battery pack 52 in the embodiment is as follows: Figure 10A This mode is also used when the ambient temperature of the battery pack 52 is lower than the first threshold or the temperature of the battery pack 52 is lower than the second threshold. In the heating mode of the battery pack 52 in this embodiment, due to the addition of the second expansion valve 17 and the air-cooled evaporator 152, it is necessary to disconnect the second expansion valve 17 and the air-cooled evaporator 152 when heating the battery pack 52 to prevent the refrigerant flowing from the second expansion valve 17 and the air-cooled evaporator 152 to the compressor 12 from containing liquid refrigerant, thereby controlling the suction superheat of the compressor 12 and improving the performance of the compressor 12. The working principle of the heat pump mode in this embodiment and the connection method with the multi-way valve 80 are the same. Figure 2 or Figure 3The basic principles are the same as in the embodiments, and can be referred to. Figure 2 or Figure 3 Examples are not described in detail here.

[0190] Figure 10B for Figure 10 A schematic diagram of the heat pump mode heating battery pack 52 of the thermal management system 1 in the embodiment.

[0191] Reference Figure 10B In the heat pump mode of this embodiment, the same Figure 4 As in this embodiment, the first throttle valve 22 needs to be disconnected to disconnect the bypass branch 20. The second expansion valve 17 can also be disconnected to disconnect the branch containing the second expansion valve 17 and the air-cooled evaporator 152. The working principle of the heat pump mode and its connection method with the multi-way valve 80 in this embodiment are the same. Figure 4 The basic principles are the same as in the embodiments, and can be referred to. Figure 4 Examples are not described in detail here.

[0192] It can be understood that in the heat pump mode of this embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened simultaneously so that the second expansion valve 17 and the branch where the air-cooled evaporator 152 is located are also connected.

[0193] Figure 10C for Figure 10 A schematic diagram of the natural heat dissipation mode of the thermal management system 1 in the embodiment for cooling the battery pack 52.

[0194] Reference Figure 10C In the natural heat dissipation mode of 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 simultaneously, and the compressor 12 does not work. The working principle of the natural heat dissipation mode in this embodiment and its connection method with the multi-way valve 80 are the same as... Figure 5 The basic principles are the same as in the embodiments, and can be referred to. Figure 5 Examples are not described in detail here.

[0195] Figure 10D for Figure 10 A schematic diagram of the compressor 12 of the thermal management system 1 in the embodiment cooling the battery pack 52 in cooling mode.

[0196] Reference Figure 10D In the heat pump mode of this embodiment, the same Figure 6 As in this embodiment, the first throttle valve 22 needs to be disconnected to disconnect the bypass branch 20. The second expansion valve 17 can also be disconnected to disconnect the branch containing the second expansion valve 17 and the air-cooled evaporator 152. The working principle of the compressor 12 in cooling mode and its connection method with the multi-way valve 80 in this embodiment are the same. Figure 6 The basic principles are the same as in the embodiments, and can be referred to. Figure 6Examples are not described in detail here.

[0197] It can be understood that in the heat pump mode of this embodiment, the first expansion valve 14 and the second expansion valve 17 can be opened simultaneously so that the second expansion valve 17 and the branch where the air-cooled evaporator 152 is located are also connected.

[0198] Figure 11 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0199] Compared to Figure 9 Thermal management system 1 in the embodiment refers to Figure 11 In this embodiment, the thermal management system 1 does not have a second throttle valve 16, and the other structures of the main circuit 10 are the same, so they will not be described again here. In this embodiment, since there is no second throttle valve 16, the ratio of the refrigerant flowing from 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 to effectively control the suction superheat of the compressor 12.

[0200] It is understood that the thermal management system 1 in this embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same, and will not be described again here.

[0201] Figure 12 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0202] Compared to Figure 10 Thermal management system 1 in the embodiment refers to Figure 12 In this embodiment, the thermal management system 1 does not have a second throttle valve 16, and the other structures of the main circuit 10 are the same. Further details will not be provided here.

[0203] It is understood that the thermal management system 1 in this embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same, and will not be described again here.

[0204] Figure 13This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0205] Compared to Figure 9 Thermal management system 1 in the embodiment refers to Figure 13 The thermal management system 1 in this embodiment and Figure 9 The main difference in the thermal management system 1 in this embodiment is that a three-way throttle valve 90a is used instead of a three-way throttle valve 90a. Figure 9 The first throttle valve 22 and the second throttle valve 16 in the embodiment. The three-way throttle valve 90a can be referred to... Figure 8 Examples are not described in detail here.

[0206] It is understood that the thermal management system 1 in this embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same, and will not be described again here.

[0207] Figure 14 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0208] Compared to Figure 10 Thermal management system 1 in the embodiment refers to Figure 14 The thermal management system 1 in this embodiment and Figure 10 The main difference in the thermal management system 1 in this embodiment is that a three-way throttle valve 90a is used instead of a three-way throttle valve 90a. Figure 10 The first throttle valve 22 and the second throttle valve 16 in the embodiment. The first throttle valve 22 and the second throttle valve 16 can be referred to... Figure 8 Examples are not described in detail here.

[0209] It is understood that the thermal management system 1 in this embodiment also includes a mode for heating the battery pack 52 (see reference). Figure 2 or Figure 3 ), heat pump mode (refer to) Figure 4 ), natural heat dissipation mode (refer to) Figure 5 ) and natural heat dissipation mode (refer to) Figure 6 And its working principle is the same. Figure 1 The operating modes in the thermal management system 1 of the embodiment are basically the same, and will not be described again here.

[0210] Figure 15This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application. For example, the thermal management system 1 in this embodiment can be applied to a vehicle.

[0211] Compared to Figure 9 Thermal management system 1 in the embodiment refers to Figure 15 The thermal management system 1 in this embodiment has the following differences.

[0212] Reference Figure 15 In some embodiments, the multi-way valve 80 in this embodiment is compared to Figure 9 In this embodiment, the multi-way valve 80 has an additional interface. 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 the 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.

[0213] It should also be noted that each port of the multi-way valve 80 in the attached diagram is marked with a number. The first port corresponds to number 1 in the attached diagram, the second port corresponds to number 2, the third port corresponds to number 3, the fourth port corresponds to number 4, the fifth port corresponds to number 5, the sixth port corresponds to number 6, the seventh port corresponds to number 7, the eighth port corresponds to number 8, and the ninth port corresponds to number 9.

[0214] Reference Figure 15 In some embodiments, there are multiple condensers 13, including air-cooled condensers 132 and liquid-cooled condensers 131. The air-cooled condenser 132 is used to exchange heat between the refrigerant flowing through it and the gas in the vehicle's cabin. The liquid-cooled condenser 131 is used to exchange heat between the refrigerant flowing through the liquid-cooled evaporator 151 and other liquids flowing through it. The liquid-cooled condenser 131 includes a first input terminal and a first output terminal connected together, as well as a second input terminal and a second output terminal connected together. The evaporator 15 includes a first input terminal and a first output terminal connected together, as well as a second input terminal and a second output terminal connected together. The compressor 12 is used to direct the refrigerant to the bypass branch 20, the input terminal of the air-cooled condenser 132, and the first input terminal of the liquid-cooled condenser 131, respectively. The evaporator 15 is used to receive the refrigerant flowing out of the bypass branch 20, the output terminal of the air-cooled condenser 132, and the first output terminal of the liquid-cooled condenser 131.

[0215] Specifically, in this embodiment, the main road 10 is compared to Figure 9 In the embodiment, the main line 10 is also equipped with a third throttle valve 18 and an air-cooled condenser 132. The third throttle valve 18 and the air-cooled condenser 132 are connected in series through the first pipeline 11. The third throttle valve 18 is used to control the flow rate of refrigerant to the air-cooled condenser 132, and the air-cooled condenser 132 is used to heat the crew cabin.

[0216] In this embodiment, the high-temperature, high-pressure gaseous refrigerant flowing out of the compressor 12 can flow not only to the bypass branch 20 where the first throttle valve 22 is located, but also to the second throttle valve 16 and the liquid-cooled condenser 131, and also to the third throttle valve 18 and the air-cooled condenser 132. The refrigerant flowing out of the branch where the second throttle 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 it can flow to the branch where the second expansion valve 17 and the liquid-cooled evaporator 151 are located.

[0217] Reference Figure 15 In some implementations, the first pump branch 60 in this embodiment and Figure 9 The structure of the first pump branch 60 in the embodiments is different.

[0218] The first pump branch 60 includes a fifth pipe 61, a first pump 62, and an electrical control assembly 64. The output end of the first pump 62 is connected to both the electrical control assembly 64 and the second input end of the liquid-cooled condenser 131 via the fifth pipe 61. In other words, the electrical control assembly 64 and the liquid-cooled condenser 131 are connected in parallel via the fifth pipe 61. The liquid flowing from the first pump 62 can flow not only to the electrical control assembly 64 but also to the liquid-cooled evaporator 151. The liquid flowing from the liquid-cooled evaporator 151 flows to the fifth port, and the liquid flowing from the electrical control assembly 64 flows to the ninth port. The second output end of the liquid-cooled condenser 131 is connected to the fifth port via the fifth pipe 61, and the electrical control assembly 64 is connected to the ninth port via the fifth pipe 61. The input end of the first pump 62 is connected to the sixth port via the fifth pipe 61.

[0219] Reference Figure 15 In some implementations, the battery pack 52 in the heat source branch 50 of this embodiment is a vehicle battery.

[0220] It is understood that any parts of the thermal management system 1 not described in this embodiment can be referred to... Figure 9 Examples are not described in detail here.

[0221] Figure 15A for Figure 15 A schematic diagram of the heating battery pack 52 of the thermal management system 1 in the embodiment.

[0222] Reference Figure 15AIn some embodiments, the thermal management system 1 includes a mode for heating the battery pack 52. This mode is mainly used in scenarios with low ambient temperatures, such as when the vehicle's ambient temperature is below a first threshold or the temperature of the battery pack 52 is below a second threshold. In this mode, the bypass branch 20 connects the output of the compressor 12 to the input of the liquid-cooled evaporator 151, the liquid-cooled condenser 131 is connected to the liquid-cooled plate of the battery pack 52 for heating the battery pack 52, and the air-cooled condenser 132 is used to heat the passenger compartment. It should be noted that the vehicle's ambient temperature at this time is equivalent to the stable environment of the vehicle's battery pack 52, that is, the atmospheric temperature inside the cavity where the battery pack 52 is placed.

[0223] Specifically, in the heated battery pack 52 mode, the second port of the multi-way valve 80 is connected to the fifth and ninth ports, and the sixth and seventh ports are connected. The second expansion valve 17 is disconnected to disconnect the branch containing the liquid-cooled evaporator 151, and the third throttle valve 18 is disconnected to disconnect the branch containing the air-cooled condenser 132.

[0224] 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) flowing out from the output end of the battery pack 52 flows to the input end of the first pump 62 through the seventh and sixth interfaces, 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 through the second output end of the liquid-cooled condenser 131 to the fifth and second interfaces, and finally flows to the input end of the battery pack 52, thus repeating the cycle. During the cycle, 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, thereby increasing the temperature of the liquid when it flows to the battery pack 52, and thus heating the battery pack 52. In addition, the liquid flowing out 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 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, it will not heat the electronic control assembly 64.

[0225] Meanwhile, part of the high-temperature, high-pressure gaseous refrigerant flowing out of the compressor 12 passes through the second throttle valve 16, the liquid-cooled condenser 131, and the first expansion valve 14, and becomes low-temperature refrigerant, flowing to the air-cooled evaporator 152. The other part passes through the bypass branch 20 where the first throttle valve 22 is located, and remains high-temperature gaseous refrigerant, flowing 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, thereby controlling the suction superheat of the compressor 12, reducing the risk of liquid carryover during suction of the compressor 12, and improving the operational reliability of the compressor 12.

[0226] It is understandable that, since the branch containing the second expansion valve 17 and the liquid-cooled evaporator 151 is disconnected, the refrigerant flowing from 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 containing the second expansion valve 17 and the liquid-cooled evaporator 151. Therefore, in the mode of heating the battery pack 52, the air-cooled evaporator 152 does not need to absorb heat from the external environment through the radiator 42. Thus, in this embodiment, any connection method between the first interface, the third interface, the fourth interface, and the eighth interface will not affect this mode. For example, in one connection method, the first interface and the third interface can be connected, and the fourth interface and the eighth interface can be connected.

[0227] Figure 15B for Figure 15 A schematic diagram of the heated passenger compartment mode of the thermal management system 1 in the embodiment.

[0228] Reference Figure 15B In some embodiments, the thermal management system 1 includes a heated passenger compartment mode. This mode is mainly used when the ambient temperature of the battery pack 52 is greater than a first threshold and the temperature of the battery pack 52 is greater than a second threshold. In this case, the bypass branch 20 is disconnected, and the output of the compressor 12 is not connected to the input of the liquid-cooled evaporator 151. The air-cooled condenser 132 is used to heat the passenger compartment.

[0229] Specifically, in this mode, the second expansion valve 17 is disconnected, thereby disconnecting the branch containing the second expansion valve 17 and the liquid-cooled evaporator 151, and the second throttle valve 16 is disconnected, thereby disconnecting the branch containing the second throttle valve 16 and the liquid-cooled condenser 131.

[0230] A portion of the high-temperature, high-pressure gaseous refrigerant flowing from compressor 12 passes through the third throttle valve 18, the air-cooled condenser 132, and the first expansion valve 14, becoming low-temperature refrigerant, and flows to the air-cooled evaporator 152. As the high-temperature gaseous refrigerant flows through the air-cooled condenser 132, it exchanges heat with the air in the passenger compartment to heat the passenger compartment. The remaining portion, after passing through the bypass branch 20 where the first throttle valve 22 is located, remains high-temperature gaseous refrigerant 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, thereby controlling the suction superheat of compressor 12, reducing the risk of liquid carryover during compressor suction, and improving the operational reliability of compressor 12.

[0231] It is understood that since the second throttle valve 16 and the second expansion valve 17 are disconnected, the coolant will not flow through the liquid-cooled condenser 131 and the liquid-cooled evaporator 151. Therefore, in this embodiment, any connection method between the various ports of the multi-way valve 80 will not affect this mode.

[0232] Figure 15C for Figure 15 A schematic diagram of the heated battery pack 52 and the crew cabin mode of the thermal management system 1 in the embodiment.

[0233] Reference Figure 15C In some embodiments, the thermal management system 1 includes a heated battery pack 52 and a passenger compartment mode. This mode is mainly used when the ambient temperature of the battery pack 52 is greater than a first threshold and the temperature of the battery pack 52 is greater than a 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 connected. The liquid-cooled condenser 131 is connected to the liquid-cooled plate of the battery pack 52 and is used to heat the battery pack 52. The air-cooled condenser 132 is used to heat the passenger compartment.

[0234] Specifically, in this mode, the second port of the multi-way valve 80 is connected to the fifth and ninth ports, and the sixth and seventh ports are connected. The second expansion valve 17 is disconnected, so that the branch containing the second expansion valve 17 and the liquid-cooled evaporator 151 is disconnected. 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) flowing out from the output end of the battery pack 52 flows to the input end of the first pump 62 through the seventh and sixth ports, 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 through the second output end of the liquid-cooled condenser 131 to the fifth and second ports, and finally flows to the input end of the battery pack 52, thus repeating the cycle. During the cycle, 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, thereby increasing the temperature of the liquid when it flows to the battery pack 52, and thus heating the battery pack 52. In addition, the liquid flowing out 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 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, it will not heat the electronic control assembly 64.

[0235] Meanwhile, the first portion of the high-temperature, high-pressure gaseous refrigerant flowing from compressor 12, after passing through the third throttle 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. As 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 portion of the high-temperature, high-pressure gaseous refrigerant flowing from compressor 12, after passing through the second throttle 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, high-pressure gaseous refrigerant flowing from compressor 12, after passing through the bypass branch 20 where the first throttle valve 22 is located, remains high-temperature gaseous refrigerant and flows to the air-cooled evaporator 152. In the air-cooled evaporator 152, high-temperature gaseous refrigerant is mixed with low-temperature refrigerant to heat the low-temperature refrigerant, thereby controlling the suction superheat of the compressor 12, reducing the risk of liquid carryover in the suction of the compressor 12, and improving the operational reliability of the compressor 12.

[0236] It is understood that since the branch where the second expansion valve 17 and the liquid-cooled evaporator 151 are located is disconnected, any connection method between the first interface, the third interface, the fourth interface and the eighth interface in this embodiment will not affect this mode.

[0237] Figure 15D for Figure 15 A schematic diagram of the heat pump heating battery and crew cabin modes of the thermal management system 1 in the embodiment.

[0238] Reference Figure 15D In some embodiments, the thermal management system 1 includes a heat pump heating battery and passenger compartment mode to heat the passenger compartment and battery pack 52. This mode is mainly used when the ambient temperature of the battery pack 52 is greater than a first threshold and the temperature of the battery pack 52 is greater than a 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 connected. The liquid-cooled condenser 131 is connected to the liquid cooling plate of the battery pack 52 to heat the battery pack 52.

[0239] Specifically, in this mode, the first and third interfaces are connected, and the fourth and eighth interfaces are connected to connect the second pump branch 70 and the heat dissipation branch 40. The second interface is connected to the fifth and ninth interfaces respectively, and the sixth and seventh interfaces are connected to connect 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 branch where the first expansion valve 14 and the air-cooled evaporator 152 are located.

[0240] At this time, a portion of the refrigerant flowing out of compressor 12 flows through the second throttle valve 16, liquid-cooled condenser 131, and second expansion valve 17, becoming low-temperature refrigerant, and flows to liquid-cooled evaporator 151. The other portion flows through the third throttle valve 18, air-cooled condenser 132, and second expansion valve 17, becoming low-temperature refrigerant again. When the high-temperature gaseous refrigerant flows through air-cooled condenser 132, it can exchange heat with the air in the passenger compartment to heat the passenger compartment. Then the low-temperature refrigerant flows through liquid-cooled evaporator 151 and returns to compressor 12.

[0241] At this time, the second pump branch 70 and the heat dissipation branch 40 are connected, so that the liquid (such as water) output from the radiator 42 flows to the second pump 72 through the first and third interfaces, then flows to the second input end of the liquid-cooled evaporator 151 through the second pump 72, and flows to the eighth and fourth interfaces through the second output end of the liquid-cooled evaporator 151, and finally flows to the radiator 42, thus repeating the cycle. During the liquid circulation process, when passing through the liquid-cooled evaporator 151, it exchanges heat with the low-temperature refrigerant in the liquid-cooled evaporator 151, which lowers the temperature of the liquid flowing from the liquid-cooled evaporator 151 to the radiator 42. When the liquid with the lower temperature flows through the radiator 42, it can exchange heat with the outside air and absorb the heat from the outside air. In this process, the heat from the outside air is used to heat the low-temperature refrigerant, so that the refrigerant is vaporized.

[0242] 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) flowing out from the output end of the battery pack 52 flows to the input end of the first pump 62 through the seventh and sixth interfaces, 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 through the second output end of the liquid-cooled condenser 131 to the fifth and second interfaces, and finally flows to the input end of the battery pack 52, thus repeating the cycle. During the cycle, 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, thereby increasing the temperature of the liquid when it flows to the battery pack 52, and thus heating the battery pack 52. In addition, the liquid flowing out 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 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, it will not heat the electronic control assembly 64.

[0243] Figure 15E for Figure 15 A schematic diagram of the natural heat dissipation mode of the thermal management system 1 in the embodiment.

[0244] Reference Figure 15EIn some embodiments, the thermal management system 1 includes a natural cooling mode to provide natural cooling for the battery pack 52 and the electronic control assembly 64. This mode is primarily used when both the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are relatively low. Figure 15D In the embodiment where the temperature is higher, the battery pack 52 requires heat dissipation. In this mode, the bypass branch 20 is disconnected, and the output of the compressor 12 is not connected to the input of the liquid-cooled evaporator 151. The radiator 42 is connected to the liquid cooling plate of the battery pack 52 to dissipate heat from the battery pack 52.

[0245] Specifically, in natural heat dissipation mode, the first and second interfaces are connected, the seventh and sixth interfaces are connected, the ninth and fifth interfaces are connected to the third interface respectively, and the eighth and fourth interfaces are connected, thereby connecting the heat source branch 50, the first pump branch 60, the second pump branch 70, and the heat dissipation branch 40 in series via the multi-way valve 80. Additionally, the compressor 12 is not operating at this time.

[0246] In this mode, liquid (e.g., water) flowing from the output of battery pack 52 flows through the seventh and sixth interfaces to the input of the first pump 62, then from the output of the first pump 62 to the second input of the liquid-cooled condenser 131, and from the second output of the liquid-cooled condenser 131 to the fifth and third interfaces, flowing to the input of the second pump 72, then from the output of the second pump 72 to the second input of the liquid-cooled evaporator 151, and from the second output of the liquid-cooled evaporator 151 to the eighth and fourth interfaces, flowing to the input of the radiator 42, and then from the output of the radiator 42 to the first and second interfaces and back to battery pack 52, thus repeating the cycle. In this mode, the liquid flowing through battery pack 52 exchanges heat with the heat emitted by battery pack 52, raising the temperature of the liquid flowing out of battery pack 52. Then, as it flows through radiator 42, it exchanges heat with the air in the external environment, lowering the temperature of the liquid after flowing through radiator 42, thereby cooling battery pack 52. Furthermore, the liquid flowing from the output of the first pump 62 can also flow to the electronic control assembly 64, and then through the ninth and second interfaces to the battery pack 52. Since the liquid flowing from the output of the first pump 62 to the electronic control assembly 64 is connected to the radiator 42, the electronic control assembly 64 can also be naturally cooled through the radiator 42. In this mode, since the compressor 12 is not working, the battery pack 52 and the motor electronic control can be cooled naturally through the radiator 42. Because the compressor 12 is not working, energy consumption can be effectively reduced.

[0247] Figure 15F for Figure 15 A schematic diagram of the compressor 12 of the thermal management system 1 in the embodiment, in cooling mode.

[0248] Reference Figure 15FIn 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 primarily used when both the ambient temperature of the battery pack 52 and the temperature of the battery pack 52 are relatively low. Figure 15E In the embodiment where the temperature is higher, the battery pack 52 also needs to dissipate heat. In this mode, the bypass branch 20 is disconnected, and the output of the compressor 12 is not connected to the input of the liquid-cooled evaporator 151. The liquid-cooled evaporator 151 is connected to the liquid cooling plate of the battery pack 52 and is used to cool the battery pack 52, while the air-cooled evaporator 152 is used to cool the passenger compartment.

[0249] Specifically, in this mode, the first and sixth interfaces are connected, and the ninth, fifth, and fourth interfaces are connected, so that the first pump branch 60 and the heat dissipation branch 40 are connected. The second and eighth interfaces are connected, and the third and seventh interfaces are connected, so that the second pump branch 70 and the heat source branch 50 are connected. 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.

[0250] At this time, the high-temperature gaseous refrigerant flowing out from the output end of the compressor 12 flows to the liquid-cooled condenser 131 through the second throttle valve 16. The refrigerant flowing out 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, while the liquid-cooled evaporator 151 can cool the liquid (such as water) flowing from the second pump 72 to the liquid-cooled evaporator 151. When the cooled liquid flows through the battery pack 52, it can cool the battery pack 52.

[0251] At the same time, since the first pump branch 60 and the heat dissipation branch 40 are connected, the heat generated by the electronic control assembly 64 can be dissipated to the environment outside the crew compartment through the radiator 42 to achieve heat dissipation of the electronic control assembly 64.

[0252] Figure 16 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0253] Compared to Figure 15 Thermal management system 1 in the embodiment refers to Figure 16 The thermal management system 1 in this embodiment and Figure 15 The main difference in the thermal management system 1 in this embodiment is that a four-way throttle valve 90b is used instead of a four-way throttle valve 90b. Figure 15 The first throttle valve 22, the second throttle valve 16, and the third throttle valve 18 in the embodiment.

[0254] Specifically, the four-way throttle valve 90b includes a first port, a second port, a third port, and a fourth port. The first port is connected to the output end of the compressor 12 via a first pipe 11. The second port is connected to the input end of the liquid-cooled condenser 131 via the first pipe 11. The third port is connected to the input end of the air-cooled condenser 132 via the first pipe 11. The fourth port is connected to the input end of the bypass branch 20 via the first pipe 11. In this embodiment, using the four-way throttle valve 90b instead of 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 potentially reducing the overall cost.

[0255] It is understood that the four-way throttle valve 90b in this embodiment has a throttling function, which can control the flow rate through the first port, the second port, the third port, and the fourth port. In some embodiments, the four-way throttle valve 90b can be a four-way expansion valve, which has a throttling and pressure-reducing function.

[0256] Figure 17 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0257] Compared to Figure 16 Thermal management system 1 in the embodiment refers to Figure 17 The thermal management system 1 in this embodiment and Figure 16 The main difference in the thermal management system 1 of this embodiment is that, in this embodiment, the output end of the bypass branch 20 is connected between the input end of the liquid-cooled evaporator 151 and the output end of the second expansion valve 17. The working principle of the thermal management system 1 in this embodiment can be referred to... Figure 16 Examples are not described in detail here.

[0258] Figure 18 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0259] Compared to Figure 15 Thermal management system 1 in the embodiment refers to Figure 18 The thermal management system 1 in this embodiment and Figure 18 The main difference in the thermal management system 1 in this embodiment is that a three-way throttle valve 90a is used instead of a three-way throttle valve 90a. Figure 15 The first throttle valve 22 and the third throttle valve 18 in this embodiment. In this embodiment, using a four-way throttle valve 90b instead of 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 potentially reducing the overall cost.

[0260] It is understood that the three-way throttle valve 90a in this embodiment has a throttling function, which can control the flow rate through the first port, the second port, and the third port. In some embodiments, the three-way throttle valve 90a can be a three-way expansion valve, which has a throttling and pressure-reducing function.

[0261] Figure 19 This is a schematic diagram of another thermal management system 1 provided in an embodiment of this application.

[0262] Compared to Figure 18 Thermal management system 1 in the embodiment refers to Figure 19 The thermal management system 1 in this embodiment and Figure 18 The main difference in the thermal management system 1 of this embodiment is that, in this embodiment, the output end of the bypass branch 20 is connected between the input end of the liquid-cooled evaporator 151 and the output end of the second expansion valve 17. The working principle of the thermal management system 1 in this embodiment can be referred to... Figure 18 Examples are not described in detail here.

[0263] It should be noted that when the thermal management system 1 in the above embodiments is applied in an energy storage cabinet, the ambient temperature of the battery pack 52 is the same as the ambient temperature of the energy storage cabinet, that is, the atmospheric temperature of the inner cavity of the cabinet used to house the battery pack 52, which can be detected by a sensor. Similarly, when the thermal management system 1 in the above embodiments is applied in a vehicle, the ambient temperature of the battery pack 52 is the same as the ambient temperature of the vehicle, that is, the atmospheric temperature of the accommodating cavity of the vehicle used to house the battery pack 52, which can also be detected by a sensor.

[0264] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A thermal management system for dissipating heat from a battery pack, characterized in that, In the thermal management system, the refrigerant output from the compressor selectively enters at least one of the liquid-cooled evaporator or the air-cooled evaporator via a bypass branch or at least one of the condensers. The output terminal of the compressor is used to connect to the input terminal of the bypass branch and the input terminal of the condenser, respectively. The output terminals of the bypass branch and the condenser are used to supply refrigerant to the input terminal of at least one of the liquid-cooled evaporator or the air-cooled evaporator. The thermal management system is used for: Selectively connect at least one of the input terminals of the bypass branch or the input terminal of the condenser to the output terminal of the compressor.

2. The thermal management system according to claim 1, characterized in that, The bypass branch includes a first throttle valve disposed on the bypass branch. The first throttle valve is used to open or close the bypass branch, or to regulate the flow rate of refrigerant input from the compressor output end through the bypass branch to at least one input end of the liquid-cooled evaporator or the air-cooled evaporator.

3. The thermal management system according to claim 1 or 2, characterized in that, The thermal management system also includes a multi-way throttle valve, which includes a first interface, a second interface, and a third interface; The first interface is used to connect to the output terminal of the compressor; The second interface is used to connect to the input end of the condenser and to control the flow rate of refrigerant from the compressor to the condenser; The third interface is used to connect to the input end of the bypass branch and to control the flow rate of refrigerant from the compressor to the bypass branch.

4. The thermal management system according to claim 1 or 2, characterized in that, The thermal management system further includes a second throttling valve for controlling the flow rate of refrigerant from the compressor to the condenser.

5. The thermal management system according to any one of claims 1-4, characterized in that, When the ambient temperature of the battery pack is less than a first threshold or the temperature of the battery pack is less than a second threshold, the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch, as well as the refrigerant input by the compressor to the condenser and output by the condenser.

6. The thermal management system according to any one of claims 1-5, characterized in that, The thermal management system also includes a radiator. When the ambient temperature of the battery pack is T1, or the temperature of the battery pack is T2, the condenser is connected to the liquid cooling plate of the battery pack for heating the battery pack. The input end of at least one of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch, as well as the refrigerant input by the compressor to the condenser and output by the condenser. When the ambient temperature of the battery pack is T3 and the temperature of the battery pack is T4, the bypass branch is disconnected, and the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant output by the condenser. The radiator is used to dissipate heat for the battery pack. When the ambient temperature of the battery pack is T5, or when the temperature of the battery pack is T6, the bypass branch is disconnected, and the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant output by the condenser. At least one of the liquid-cooled evaporator or air-cooled evaporator is connected to the liquid cooling plate of the battery pack, and at least one of the liquid-cooled evaporator or air-cooled evaporator is used to cool the battery pack. Where T1 < first threshold < T3 < T5, T2 < second threshold < T4 < T6.

7. The thermal management system according to any one of claims 1-6, characterized in that, The bypass branch includes a first throttle valve disposed on the bypass branch. The first throttle valve is used to open or close the bypass branch, or to regulate the flow rate of refrigerant input from the compressor output terminal through the bypass branch to at least one input terminal of the liquid-cooled evaporator or the air-cooled evaporator. The thermal management system further includes a sensor and a controller. The sensor is used to detect at least one of the temperature and pressure of the refrigerant input to the compressor. The controller is used to control the first throttle valve to regulate the flow rate of refrigerant input from the compressor output terminal through the bypass branch to at least one input terminal of the liquid-cooled evaporator or the air-cooled evaporator based on at least one of the temperature and pressure of the refrigerant input to the compressor detected by the sensor.

8. The thermal management system according to claim 7, characterized in that, The controller is used to control the first throttle valve to regulate the flow rate of refrigerant input from the compressor output to at least one of the liquid-cooled evaporator or air-cooled evaporator through the bypass branch, based on at least one of the temperature and pressure of the refrigerant input to the compressor detected by the sensor, the ambient temperature of the battery pack, or the temperature of the battery pack.

9. An energy storage device, characterized in that, The energy storage device includes a battery pack and a thermal management system as described in any one of claims 1-8, the thermal management system being used to regulate the temperature of the battery pack or to regulate the temperature of the energy storage device.

10. The energy storage device according to claim 9, characterized in that, When the ambient temperature of the energy storage device is less than a first threshold or the temperature of the battery pack is less than a second threshold, the input terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator receives the refrigerant transmitted by the compressor through the bypass branch, as well as the refrigerant input by the compressor to the condenser and output by the condenser.

11. The energy storage device according to claim 9 or 10, characterized in that, The energy storage device also includes a power module, which is used to convert the electrical energy output by the battery pack into power. The second input terminal and the second output terminal of at least one of the liquid-cooled evaporator or air-cooled evaporator are connected to the liquid cooling plate of the power module for heat dissipation of the power module.

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

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