Energy storage system thermal management system with thermal circulation

Abstract

The utility model discloses an energy storage system thermal management system with thermal circulation, the energy storage system comprises an energy storage component and a heat transfer component, the heat transfer component is provided with a first port, a second port and a fluid channel communicated with the first port and the second port, the first port and the second port can be connected with the heat management system through a first pipeline and a second pipeline, and the heat management system comprises a gas compressor, heat exchangers and a valve assembly. The second heat exchanger is provided with a heat dissipation mechanism for heat exchange between the refrigerant and the surrounding environment, the first heat exchanger is provided with a fan and an air inlet, and the heat dissipation mechanism is arranged at the air inlet and located on an air inlet path of the first heat exchanger. The heat energy released by the second heat exchanger can be reused by the first heat exchanger, so that cyclic utilization of the heat energy is realized, and the energy efficiency is improved.

Description

Technical Field

[0001] The utility model relates to a thermal management system for an energy storage system with a thermal cycle. Background Art

[0002] An energy storage system is a device or system capable of storing energy. It can store excess energy and use it when needed. Energy storage systems are usually used to improve energy utilization efficiency, reduce energy waste, and improve power grid stability. Energy storage systems can include devices or technologies such as batteries, supercapacitors, flywheels, and hydraulic systems, among which batteries are one of the most commonly used energy storage methods. Energy storage systems can be used in various application scenarios, such as power grid peak shaving, renewable energy grid connection, electric vehicle charging, and home energy storage.

[0003] During the operation of the energy storage system, overcooling or overheating can cause failures of the energy storage system. Therefore, it is necessary to set up a thermal management system to manage the heat of the energy storage system. The design of the thermal management system needs to consider various factors, including the heating power of the battery, the thermal insulation design of the container, and the thermal management control strategy. Thermal management is crucial for the energy storage system. It can prevent the battery from overheating, extend the battery life, and reduce safety risks. With the development of the energy storage industry, thermal management technology is also constantly being studied and improved to meet the requirements of higher energy density, more efficient and balanced heat dissipation, higher reliability and stability, lower energy consumption, and lower cost.

[0004] In the prior art, most energy storage systems are provided with independent heating mechanisms to provide the function of heating up, and the heating methods adopted by the heating mechanisms are mainly electric heating, with high energy consumption and low heating efficiency. The existing thermal management systems for energy storage systems generally have deficiencies such as limited overall energy efficiency, complex system structure, high cost, and uneven surface temperature of the cold plates or heating plates of the battery boxes. At the same time, during the operation of the thermal management system, a large amount of heat energy will be released to the external environment. In the existing thermal management systems, the released heat energy cannot be utilized, resulting in a large amount of heat energy being wasted and the low energy utilization rate of the thermal management system. Summary of the Utility Model

[0005] The purpose of the utility model is to provide a new thermal management system with a thermal cycle, which can realize the recycling of heat energy and improve the energy efficiency of the thermal management system.

[0006] To achieve the above object, the technical solution adopted by the present utility model is as follows: A thermal management system for an energy storage system with a thermal cycle. The energy storage system includes an energy storage component and a heat transfer component. The heat transfer component has a first port, a second port, and a fluid channel connecting the first port and the second port. The first port and the second port can be connected to the thermal management system through a first pipeline and a second pipeline. The thermal management system includes a gas compressor, a heat exchanger, and a valve assembly. The heat exchanger includes a first heat exchanger and a second heat exchanger arranged adjacent to each other. The second heat exchanger has a heat dissipation mechanism for the heat exchange fluid to exchange heat with the surrounding environment. The first heat exchanger has a fan and an air inlet. The heat dissipation mechanism is arranged at the air inlet, and the heat dissipation mechanism is located on the air inlet path of the first heat exchanger.

[0007] In some embodiments, the outlet of the gas compressor, the second heat exchanger, and the second pipeline are sequentially connected through pipelines to form a heating path for supplying the heat exchange fluid with a preset temperature to the heat transfer component; the first pipeline, the first heat exchanger, and the inlet of the gas compressor are sequentially connected through pipelines to form a heating return path for recovering the heat exchange fluid. The heating path, the fluid channel in the heat transfer component, and the heating return path constitute a heating circulation path. A first electronic expansion valve is provided on the pipeline between the outlet of the gas compressor and the second heat exchanger.

[0008] In some embodiments, the thermal management system further includes a detection and control module. The detection and control module includes a controller, a temperature sensor arranged in the pipeline of the thermal management system and electrically connected or signal-connected to the controller. The temperature sensor is arranged on the pipeline between the second heat exchanger and the second pipeline. The controller is configured to be able to obtain the data of the temperature sensor and adjust the opening degree of the first electronic expansion valve according to the obtained data.

[0009] In some embodiments, the pipeline between the outlet of the gas compressor and the second heat exchanger and the pipeline between the second heat exchanger and the second pipeline are connected through a branch pipeline. The branch pipeline has a first end and a second end provided at both ends. The first end is connected to the pipeline between the gas compressor and the second heat exchanger, and the second end is connected to the pipeline between the second heat exchanger and the second pipeline. The first electronic expansion valve is arranged on the pipeline between the first end of the branch pipeline and the second heat exchanger. The temperature sensor is arranged on the pipeline between the second end of the branch pipeline and the second pipeline.

[0010] In some embodiments, the thermal management system further includes a detection and control module. The detection and control module includes a controller, and a pressure sensor disposed in the pipeline of the thermal management system and electrically or signal-connected to the controller. The pressure sensor includes a first pressure sensor disposed at the inlet of the gas compressor and a second pressure sensor disposed at the outlet of the gas compressor. The controller is electrically or communicatively connected to the gas compressor, and the controller is configured to adjust the rotational speed of the gas compressor according to the detection value of the pressure sensor. The controller is also electrically or communicatively connected to the valve assembly, and the controller is configured to control the opening and closing and / or the opening degree of the valve according to a preset program.

[0011] In some embodiments, the valve assembly includes a first solenoid valve disposed on the pipeline between the outlet of the gas compressor and the second heat exchanger, and a second solenoid valve disposed on the pipeline between the inlet of the compressor and the first heat exchanger. When the first solenoid valve and the second solenoid valve are opened, the heating circulation path is opened.

[0012] In some embodiments, the thermal management system further includes the heat exchange fluid; and / or, the heat exchange fluid is a refrigerant or a fluid other than a refrigerant.

[0013] In some embodiments, the heat exchange fluid is refrigerant R134a, refrigerant R1234yf, refrigerant R410A, refrigerant R513A, refrigerant R513B or refrigerant R454B.

[0014] In some embodiments, the first heat exchanger further has a heat exchange chamber, an air outlet, and a heat exchange mechanism. The air inlet and the air outlet communicate with the heat exchange chamber. The fan is disposed at the air outlet. The heat exchange mechanism is located in the heat exchange chamber, and the heat exchange mechanism is connected to the gas compressor through a pipeline. The heat exchange mechanism is configured to allow the heat exchange fluid introduced therein to perform heat exchange in the heat exchange chamber.

[0015] In some embodiments, the heat exchange fluid in the fluid channel is in a gas-liquid two-phase equilibrium state.

[0016] In some embodiments, the thermal management system further includes a fluid storage tank and a recuperator. The outlet of the gas compressor, the first heat exchanger, the fluid storage tank, the recuperator, and the first pipeline are sequentially connected through pipelines to form a cooling path for supplying a heat exchange fluid with a preset temperature to the heat transfer component. A first electronic expansion valve is provided on the pipeline between the first fluid path of the recuperator and the first pipeline; the second pipeline, the recuperator, and the inlet of the gas compressor are sequentially connected through pipelines to form a cooling return path for recovering the heat exchange fluid, and the cooling path, the fluid channel in the heat transfer component, and the cooling return path constitute a cooling circulation path.

[0017] In some embodiments, the fluid channel includes a plurality of first channels arranged in parallel along a first direction, and second channels connected between the first channels, such that the pressure difference when the fluid flows from the first port through the fluid channel to the second port is less than a preset value; and / or, the projection of the energy storage component on the heat transfer component falls within the distribution range of the fluid channel.

[0018] In some embodiments, along a second direction perpendicular to the first direction, the first channels are connected to the second channels to form a plurality of rectangular circuits distributed at intervals. The fluid channel includes a third channel connected between the two outermost rectangular circuits in the second direction. The first port is provided on the third channel. Adjacent two rectangular circuits are connected through a fourth channel, and along the second direction, the fourth channels are alternately distributed on different sides of the rectangular circuits along the first direction. The second port is provided on the fourth channel.

[0019] Due to the application of the above technical solutions, the present utility model has the following advantages compared with the prior art: In the thermal management system of the present utility model, the heat energy released by the second heat exchanger can enter the first heat exchanger through the air inlet and participate in the heat exchange work of the first heat exchanger, so that the released heat energy is effectively utilized. Not only the recycling of energy is realized, but also the heat exchange effect of the first heat exchanger can be improved, and the energy efficiency of the thermal management system can be improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Attached Figure 1 is a schematic diagram of the thermal management system of Embodiment 1 of the present utility model in the heating mode;

[0021] Attached Figure 2 is a schematic diagram of the thermal management system of Embodiment 1 of the present utility model in the cooling mode;

[0022] Attached Figure 3 is a schematic diagram of the thermal management system of Embodiment 1 of the present utility model in the defrosting mode;

[0023] Appended Figure 4 is a schematic diagram of the thermal management system according to Embodiment 2 of the present utility model;

[0024] Appended Figure 5 is a schematic diagram of the thermal management system according to Embodiment 3 of the present utility model;

[0025] Appended Figure 6 is a schematic diagram of the thermal management system according to Embodiment 4 of the present utility model;

[0026] Appended Figure 7 is a schematic diagram of the second setting method of the heat transfer component of the present utility model;

[0027] Appended Figure 8 is a schematic diagram of the third setting method of the heat transfer component of the present utility model;

[0028] Appended Figure 9 is a schematic diagram of the fluid channel of the present utility model;

[0029] Appended Figure 10 is a schematic diagram of the overall structure according to Embodiment 5 of the present utility model;

[0030] Appended Figure 11 is a schematic diagram of the overall control structure of the refrigeration control system according to Embodiment 5 of the present utility model;

[0031] Appended Figure 12 is a schematic diagram of the overall control structure of the heating control system according to Embodiment 5 of the present utility model;

[0032] Appended Figure 13 is a schematic diagram of the overall control structure of the defrosting system according to Embodiment 5 of the present utility model;

[0033] Appended Figure 14 is a temperature distribution diagram of the refrigeration operation system according to Embodiment 5 of the present utility model;

[0034] Appended Figure 15 is a temperature distribution diagram of the heating operation system according to Embodiment 5 of the present utility model;

[0035] Appended Figure 16 is a comparison diagram of the inlet and outlet temperatures of the liquid cooling plate and the inlet and outlet temperatures of the direct cooling plate according to Embodiment 5 of the present utility model;

[0036] Appended Figure 17 is a schematic diagram of the efficiency improvement - reverse Carnot cycle energy efficiency comparison according to Embodiment 5 of the present utility model. Detailed implementation manners

[0037] The technical solution of the present utility model will be elaborated in detail below in conjunction with the accompanying drawings and specific embodiments, so that the advantages and features of the present utility model are more easily understood by those skilled in the art. Obviously, the described embodiments of the present application are only a part of the embodiments of the present application, rather than all embodiments. All other embodiments obtained by those skilled in the art without creative work based on the embodiments in the present application belong to the scope of protection of the present application.

[0038] Embodiment 1

[0039] An energy storage system includes an energy storage box and a heat transfer component 200 for heat exchange of the energy storage box. To ensure the normal operation of the energy storage box and guarantee its working efficiency, heat exchange of the energy storage box can be performed through the heat transfer component 200. The heat transfer component 200 has a first port 210 and a second port 220, and a fluid channel 230 connecting the first port 210 and the second port 220. In this embodiment, the energy storage box includes an energy storage component 100, and the heat transfer component 200 is in contact with the energy storage component 100 for heat exchange. Specifically, in this embodiment, the energy storage component 100 is an energy storage battery pack.

[0040] See Figures 1 to 3 A thermal management system of an energy storage system with a heat cycle as shown, which is used to control and manage the temperature of the energy storage system. Among them, the first port 210 and the second port 220 of the heat transfer component 200 can be connected to the thermal management system through a first pipeline 910 and a second pipeline 920. The thermal management system can introduce refrigerants at different temperatures into the heat transfer component 200, and the refrigerant introduced into the heat transfer component 200 directly exchanges heat with the energy storage component 100, with higher heat exchange efficiency.

[0041] The thermal management system includes a gas compressor 300, a heat exchanger 500, and a valve assembly. Among them, the gas compressor 300 is used to pressurize the heat exchange fluid and discharge the heat exchange fluid in a high-temperature and high-pressure gas state. The heat exchanger 500 is used to perform heat exchange processing on the heat exchange fluid before it enters the heat transfer component 200 and after it is discharged from the heat transfer component 200. It includes a first heat exchanger 510 and a second heat exchanger 520 arranged adjacent to each other. The second heat exchanger 520 has a heat dissipation mechanism for the heat exchange fluid to exchange heat with the surrounding environment. The first heat exchanger 510 has an air inlet, and the heat dissipation mechanism is arranged at the air inlet and is located on the air inlet path of the first heat exchanger 510. With such an arrangement, the heat dissipated by the second heat exchanger 520 will enter the first heat exchanger 510 through the air inlet and participate in the heat exchange work of the first heat exchanger 510, realizing the recycling of thermal energy and improving the heat exchange efficiency of the first heat exchanger 510.

[0042] In this embodiment, the gas compressor 300, the second heat exchanger 520, and the second pipeline 920 are connected through pipelines to form a heating path for supplying a heat exchange fluid with a preset temperature to the heat transfer component 200. Specifically, the outlet of the gas compressor 300 is connected to the second heat exchanger 520 through a pipeline. A first electronic expansion valve 810 is provided on the pipeline between the outlet of the gas compressor 300 and the second heat exchanger 520 for controlling the flow rate of the heat exchange fluid passing through the second heat exchanger 520. The first pipeline 910, the first heat exchanger 510, and the gas compressor 300 are sequentially connected through pipelines to form a heating return path for recovering the heat exchange fluid. The heating path, the fluid channel 230 in the heat transfer component 200, and the heating return path constitute a heating circulation path. When the temperature of the energy storage component 100 is lower than the first temperature, the heating circulation path is connected, and the heat exchange fluid circulates in the heating circulation path and continuously heats the energy storage component, and the thermal management system turns on the heating mode. In a preferred embodiment, the first temperature is 15 to 35 degrees Celsius, and the preset temperature is above 10 degrees Celsius and below 45 degrees Celsius.

[0043] See Figure 1 As shown, in this embodiment, the pipeline between the gas compressor 300 and the second heat exchanger 520 and the pipeline between the second heat exchanger 520 and the second pipeline 920 are connected through a branch pipeline 950. Specifically, the branch pipeline 950 has a first end and a second end disposed at both ends. The first end is connected to the pipeline between the gas compressor 300 and the second heat exchanger 520, and the second end is connected to the pipeline between the second heat exchanger 520 and the second pipeline 920. When the heat exchange fluid flows through the connection between the end of the branch pipeline 950 and the above pipeline, it will be split. Part of the heat exchange fluid flows through the second heat exchanger 520 for heat exchange, and the other part of the heat exchange fluid bypasses the second heat exchanger 520 through the branch pipeline 950. The first electronic expansion valve 810 is provided on the pipeline between the first end of the branch pipeline 950 and the second heat exchanger 520. The gas compressor 300, the second heat exchanger 520 / branch pipeline 950, and the second pipeline 920 are connected to form the above heating path.

[0044] In this embodiment, the thermal management system further includes a gas-liquid separator 400, a fluid storage tank 700, and a detection and control module. Among them, the gas-liquid separator 400 is used to separate gas and liquid; the demand for the heat exchange fluid by the system is different under different operating modes, and the fluid storage tank 700 can play a role in temporarily storing the heat exchange fluid. The detection and control module includes a controller and a pressure sensor disposed in the pipeline of the thermal management system and electrically connected or signal-connected to the controller. The first pipeline 910, the fluid storage tank 700, the first heat exchanger 510, the gas-liquid separator 400, and the gas compressor 300 are sequentially connected through pipelines to form a heating return path for recovering the heat exchange fluid.

[0045] In the heating mode, the heat exchange fluid discharged by the gas compressor 300 flows through the gas compressor 300, the second heat exchanger 520 and the second pipeline 920 in sequence. Among them, the heat exchange fluid is branched at the first end of the branch pipeline 950 and mixed together again at the second end of the branch pipeline 950. The heat exchange fluid flowing through the second pipeline 920 flows into the fluid channel 230 from the second port 220, and after heat exchange with the energy storage component 100, it flows out from the first port 210. Then it flows through the first pipeline 910, the fluid storage tank 700, the first heat exchanger 510 and the gas-liquid separator 400 in sequence. Finally, the heat exchange fluid flows back into the gas compressor 300. At this time, a cycle is completed and the next cycle starts. In this mode, the second port 220 is the inlet of the heat transfer component 200, and the first port 210 is the outlet of the heat transfer component 200.

[0046] In this embodiment, the thermal management system includes a heat exchange fluid. In some embodiments, the heat exchange fluid is a refrigerant or a fluid other than a refrigerant. In this embodiment, the heat exchange fluid is a refrigerant in a gas-liquid two-phase equilibrium state at a preset temperature. In some embodiments, the thermal management system does not include a refrigerant.

[0047] In this embodiment, the heat exchange fluid in the fluid channel 230 is in a gas-liquid two-phase equilibrium state. Specifically, the fluid channel 230 has such a shape that the pressure difference when the fluid flows from the first port 210 through the fluid channel to the second port 220 is less than a preset value, so as to be able to control the pressure drop between the first port 210 and the second port 220. After the refrigerant is introduced into the fluid channel 230 in this way, in the state of gas-liquid two-phase equilibrium and when the pressure drop difference between the first port 210 and the second port 220 is controlled within a preset range, the temperature difference of the refrigerant between the first port 210 and the second port 220 can be controlled, so that the temperature of the refrigerant in the fluid channel 230 is uniform and the heat exchange effect between the refrigerant and the energy storage component 100 is better.

[0048] In this embodiment, the heat exchange fluid is preferably selected from refrigerants R134a, R1234yf, R410A, R513A, R513B, and R454B. When R134a is used as the refrigerant, the heat transfer component 200 with a pressure difference less than 19 kPa between the first port 210 and the second port 220 is selected; when R1234yf is used as the refrigerant, the heat transfer component 200 with a pressure difference less than 19 kPa between the first port 210 and the second port 220 is selected; when R410A is used as the refrigerant, the heat transfer component 200 with a pressure difference less than 20 kPa between the first port 210 and the second port 220 is selected; when R513A is used as the refrigerant, the heat transfer component 200 with a pressure difference less than 20 kPa between the first port 210 and the second port 220 is selected; when R513B is used as the refrigerant, the heat transfer component 200 with a pressure difference less than 43 kPa between the first port 210 and the second port 220 is selected; when R454B is used as the refrigerant, the heat transfer component 200 with a pressure difference less than 40 kPa between the first port 210 and the second port 220 is selected.

[0049] In this embodiment, in the heating cycle path, a part of the high-temperature and high-pressure gaseous refrigerant discharged by the gas compressor 300 condenses into a liquid state in the second heat exchanger 520, and a part directly flows through the branch pipeline 950. In the pipeline between the gas compressor 300 and the second heat exchanger 520, the refrigerant is in a high-temperature and high-pressure gas state. At the second end of the branch pipeline 950, the liquid refrigerant and the gaseous refrigerant are mixed together to form a gas-liquid two-phase refrigerant, specifically a medium-temperature and high-pressure gas-liquid two-phase refrigerant. The refrigerant in this state is introduced into the heat transfer component 200 through the second pipeline 920. Therefore, in the pipeline between the second end and the second pipeline 920, and in the second pipeline 920 and the fluid passage 230, the refrigerant is in a medium-temperature and high-pressure gas-liquid two-phase equilibrium state. After the refrigerant flows into the first heat exchanger 510 from the first port 210, the first heat exchanger 510 evaporates the refrigerant, completely converting the refrigerant into a gaseous state, and then introducing it into the gas compressor 300 through the gas-liquid separator 400. In the pipeline between the gas-liquid separator 400 and the gas compressor 300, the refrigerant is in a medium-temperature and high-pressure gas state.

[0050] In this embodiment, since the refrigerant condenses in the second heat exchanger 520, a large amount of heat energy will be generated during the process. At the same time, the refrigerant needs to evaporate in the first heat exchanger 510 and requires a large amount of heat energy. Therefore, the heat energy generated in the second heat exchanger 520 is introduced into the first heat exchanger 510 to achieve the recycling of heat energy. In this embodiment, the first heat exchanger 510 further has a heat exchange chamber and an air outlet. The air outlet is communicated with the air inlet to the heat exchange chamber, and a fan is arranged in the air outlet to circulate the air. The first heat exchanger further has a heat exchange mechanism. The heat exchange mechanism is located in the heat exchange chamber, and the heat exchange mechanism is connected to the gas compressor 300 through a pipeline. The heat exchange fluid is introduced into the heat exchange mechanism and exchanges heat with the air in the heat exchange chamber.

[0051] In this embodiment, the thermal management system further includes a regenerator 600. The regenerator 600 is also used for heat exchange treatment of the heat exchange fluid. It has a first fluid passage 610 and a second fluid passage 620 that are independent of each other but can exchange heat with each other. In the heating return passage, the first pipeline 910, the fluid storage tank 700, the first fluid passage 610 of the regenerator 600, the first heat exchanger 510, the gas-liquid separator 400, and the gas compressor 300 are sequentially connected through pipelines. The heat exchange fluid discharged from the heat transfer component 200 flows through the first fluid passage 610 of the regenerator 600 and then flows into the first heat exchanger 510 for evaporation treatment.

[0052] In this embodiment, refer to Figure 2 As shown, the gas compressor 300, the first heat exchanger 510, the fluid storage tank 700, the first fluid passage 610 of the regenerator 600, and the first pipeline 910 are sequentially connected through pipelines to form a cooling passage for supplying the refrigerant with a second preset temperature to the heat transfer component 200. Specifically, the outlet of the gas compressor 300 is connected to the first heat exchanger 510 through a pipeline. A second electronic expansion valve 820 is provided on the pipeline between the first fluid passage 610 of the regenerator 600 and the first pipeline 910. The second electronic expansion valve 820 can regulate the pressure of the refrigerant introduced into the heat transfer component 200, and the second electronic expansion valve 820 can cooperate with the gas compressor 300 to adjust the flow rate of the refrigerant introduced into the heat transfer component 200. The second pipeline 920, the second fluid passage 620 of the regenerator 600, the gas-liquid separator 400, and the gas compressor 300 are sequentially connected through pipelines to form a cooling return passage for recovering the refrigerant. Specifically, the gas-liquid separator 400 is connected to the inlet of the gas compressor 300 through a pipeline.

[0053] The cooling passage, the fluid passage 230 in the heat transfer component 200, and the cooling return passage constitute a cooling circulation passage. When the temperature of the energy storage component 100 is higher than the second temperature, the refrigerant circulates in the cooling circulation passage and continuously cools the energy storage component 100, and the thermal management system turns on the cooling mode. In a preferred embodiment, the second temperature is 15 to 35 degrees Celsius, and the second preset temperature is above 10 degrees Celsius and below 45 degrees Celsius.

[0054] In the cooling mode, the refrigerant discharged by the gas compressor 300 sequentially flows through the first heat exchanger 510, the fluid storage tank 700, the first fluid passage 610 of the regenerator 600, and the first pipe 910, and enters the fluid passage 230 of the heat transfer component 200 from the first port 210. After the refrigerant in the fluid passage 230 exchanges heat with the energy storage component 100, it flows out from the second port 220, and then sequentially flows through the second pipe 920, the second fluid passage 620 of the regenerator 600, and the gas-liquid separator 400. Finally, the refrigerant flows back into the gas compressor 300, and at this time, one cycle is completed and the next cycle begins. In this mode, the first port 210 is the inlet of the heat transfer component 200, and the second port 220 is the outlet of the heat transfer component 200.

[0055] In this embodiment, the second preset temperature is less than the preset temperature, and the refrigerant is also in a gas-liquid two-phase equilibrium state at the second preset temperature. In some embodiments, the refrigerant introduced into the cooling circulation passage and the heating circulation passage is the same. In other embodiments, the refrigerant introduced into the cooling circulation passage and the heating circulation passage is different. In this embodiment, the same refrigerant is introduced into the cooling circulation passage and the heating circulation passage.

[0056] In this embodiment, in the cooling circulation path, the refrigerant discharged by the gas compressor 300 is in a high-temperature and high-pressure gas state. In the pipeline between the gas compressor 300 and the first heat exchanger 510, the refrigerant is still in a high-temperature and high-pressure gas state. The first heat exchanger 510 cools the flowing refrigerant, so that after the cooling treatment, in the pipeline between the first heat exchanger 510 and the first fluid passage 610 of the regenerator 600, the refrigerant is in a medium-temperature and high-pressure liquid state. The refrigerant flowing through the first fluid passage 610 of the regenerator 600 will be further cooled, so that in the pipeline between the first fluid passage 610 of the regenerator 600 and the second electronic expansion valve 820, the refrigerant is in a low-temperature and high-pressure liquid state. The second electronic expansion valve 820 releases the pressure of the refrigerant, so that the refrigerant flowing through the second electronic expansion valve 820 is converted into a low-temperature and low-pressure gas-liquid two-phase state, and the refrigerant in the first pipeline 910 and the fluid passage 230 is in a low-temperature and low-pressure gas-liquid two-phase equilibrium state. The refrigerant flowing out of the second port 220 is still in a liquid-carrying state. Then the refrigerant flows through the second fluid passage 620 of the regenerator 600, and the medium-temperature and high-pressure refrigerant in the first fluid passage 610 exchanges heat with the refrigerant in the second fluid passage 620, so that all the refrigerant in the second fluid passage 620 is converted into a gaseous state. The gas-liquid separator 400 provided between the second fluid passage 620 and the gas compressor 300 further separates the liquid refrigerant in the pipeline, improving the safety performance. In the pipeline between the gas-liquid separator 400 and the gas compressor 300, the refrigerant is in a low-temperature and low-pressure gas state. This ensures that the refrigerant introduced into the gas compressor 300 is in a fully gaseous state, guaranteeing the normal operation of the gas compressor 300. Then the gas compressor 300 pressurizes the introduced refrigerant and discharges the high-temperature and high-pressure gaseous refrigerant, thus starting the second cycle.

[0057] The thermal management system of the energy storage system in this embodiment also has a defrosting mode for removing the frost condensed on the surface of the first heat exchanger 510, and the cooling mode can be directly used for defrosting. Specifically, in the refrigeration mode, the first heat exchanger 510 exchanges heat with the flowing refrigerant through the circulating air, and it includes a fan 511 for circulating the air. In the defrosting mode, the fan 511 is turned off, and the refrigerant directly exchanges heat with the frost attached to the first heat exchanger 510 and plays a role in removing the frost during the heat exchange process.

[0058] In the thermal management system, the gas compressor 300, the first heat exchanger 510, the fluid storage tank 700, the first fluid passage 610 of the regenerator 600, the second electronic expansion valve 820, the gas-liquid separator 400, and the gas compressor 300 are also connected in sequence through pipelines to form a defrosting circulation path. The refrigerant circulates in the defrosting circulation path, and can eliminate the ice and frost condensed on the surface of the first heat exchanger. Specifically, in the defrosting mode, the high-temperature and high-pressure gaseous refrigerant discharged by the gas compressor 300 flows through the first heat exchanger 510 to eliminate the attached ice and frost, and then the refrigerant returns to the gas compressor 300 to complete a cycle.

[0059] In this embodiment, stop valves 830 are provided on both the first pipeline 910 and the second pipeline 920. Before connecting the thermal management system to the heat transfer component 200, the two stop valves 830 are in a closed state. After connecting the thermal management system to the heat transfer component 200 through the first pipeline 910 and the second pipeline 920, the stop valves 830 are opened.

[0060] In this embodiment, the controller can control the opening and closing and the opening degree of the valves included in the thermal management system according to a preset program, so that the thermal management system operates in different modes. Specifically, the thermal management system of the energy storage system includes a valve assembly for controlling the opening and closing of the pipeline. The valve assembly includes a first solenoid valve 841 provided on the pipeline between the outlet of the gas compressor 300 and the second heat exchanger 520, a second solenoid valve 842 provided on the pipeline between the inlet of the gas compressor 300 and the first heat exchanger 510. Specifically, the second solenoid valve 842 is provided on the pipeline between the gas-liquid separator 400 and the first heat exchanger 510, a third solenoid valve 843 provided on the pipeline between the outlet of the gas compressor 300 and the first heat exchanger 510, a fourth solenoid valve 844 provided on the pipeline between the second pipeline 920 and the second fluid passage 620 of the regenerator 600, and a fifth solenoid valve 845 provided on the pipeline between the first electronic expansion valve 810 and the gas-liquid separator 400.

[0061] The controller is electrically connected to the valve assembly and can control the opening or closing of the solenoid valve. When the thermal management system is used to manage the heat of the energy storage system, when the temperature of the energy storage component 100 is lower than the preset temperature, the controller controls the first solenoid valve 841 and the second solenoid valve 842 to open, and controls the third solenoid valve 843, the fourth solenoid valve 844 and the fifth solenoid valve 845 to close, so that the heating circulation path is connected and the heating mode is started. When the temperature of the energy storage component 100 is higher than the preset temperature, the controller controls the third solenoid valve 843 and the fourth solenoid valve 844 to open, and controls the first solenoid valve 841, the second solenoid valve 842 and the fifth solenoid valve 845 to close, so that the cooling circulation path is connected and the cooling mode is started. When the controller controls the third solenoid valve 843 and the fifth solenoid valve 845 to open, and the first solenoid valve 841, the second solenoid valve 842 and the fourth solenoid valve 844 to close, the defrosting circulation path is connected and the defrosting mode is started.

[0062] In this embodiment, the pressure sensors include a first pressure sensor disposed at the inlet of the gas compressor 300 and a second pressure sensor disposed at the outlet of the gas compressor 300. The controller is electrically or communicatively connected to the gas compressor 300 and the valve included in the thermal management system, and the controller can adjust the rotation speed of the gas compressor according to the detection values of the pressure sensors. Specifically, the first pressure sensor can obtain the pressure value P1 at the inlet of the gas compressor 300, and the second pressure sensor can obtain the pressure value P2 at the outlet of the gas compressor 300.

[0063] In the heating mode, compare the saturation temperature Tp2 of the refrigerant at the P2 pressure value with the preset temperature:

[0064] When Tp2 is lower than the preset temperature range, increase the rotation speed of the gas compressor,

[0065] When Tp2 is higher than the preset temperature range, decrease the rotation speed of the gas compressor.

[0066] In the cooling mode, compare the saturation temperature Tp1 of the refrigerant at the P1 pressure value with the second preset temperature:

[0067] When Tp1 is lower than the second preset temperature range, decrease the rotation speed of the gas compressor;

[0068] When Tp1 is higher than the second preset temperature range, increase the rotation speed of the gas compressor.

[0069] In this embodiment, the thermal management system of the energy storage system includes a first check valve 851 and a second check valve 852 that only allow the refrigerant to flow unidirectionally into the fluid storage tank 700, a third check valve 853 that only allows the refrigerant to flow unidirectionally from the second electronic expansion valve 820 to the first pipeline 910, and a fourth check valve 854 that only allows the refrigerant to flow unidirectionally from the second electronic expansion valve 820 to the first heat exchanger 510. The first check valve 851 is arranged on the pipeline between the first heat exchanger 510 and the fluid storage tank 700, the second check valve 852 is arranged on the pipeline between the first pipeline 910 and the fluid storage tank 700, the third check valve 853 is arranged on the pipeline between the first pipeline 910 and the second electronic expansion valve 820, and the fourth check valve 854 is arranged on the pipeline between the first heat exchanger 510 and the second electronic expansion valve 820.

[0070] In the cooling mode, the first check valve 851 and the third check valve 853 are opened, and the second check valve 852 and the fourth check valve 854 are closed. The cooling passage and the cooling return passage are automatically connected, and a cooling circulation passage is automatically formed. In the heating mode, the second check valve 852 and the fourth check valve 854 are opened, and the first check valve 851 and the third check valve 853 are closed. The heating passage and the heating return passage are automatically connected, and a heating circulation passage is automatically formed.

[0071] In this embodiment, the thermal management system of the energy storage system includes temperature sensors. The temperature sensors include a first temperature sensor arranged on the pipeline between the second end of the branch pipeline 950 and the second pipeline 920, a second temperature sensor arranged on the pipeline between the first fluid passage 610 of the regenerator 600 and the second electronic expansion valve 820, a third temperature sensor arranged on the pipeline between the first fluid passage 610 of the regenerator 600 and the fluid storage tank 700, a fourth temperature sensor arranged on the pipeline between the second fluid passage 620 of the regenerator 600 and the second pipeline 920, and a fifth temperature sensor arranged at the inlet of the gas compressor 300. Among them, the first temperature sensor is used to obtain the temperature T1 of the refrigerant in the pipeline between the second heat exchanger 520 and the second pipeline 920, the second temperature sensor is used to obtain the temperature T2 at the outlet of the first fluid passage 610 of the regenerator 600, the third temperature sensor is used to obtain the temperature T3 at the inlet of the first fluid passage 610 of the regenerator 600, the fourth temperature sensor is used to obtain the temperature T4 at the inlet of the second fluid passage 620 of the regenerator 600, and the fifth temperature sensor is used to obtain the temperature T5 at the inlet of the gas compressor 300.

[0072] In this embodiment, the controller is electrically connected or communicatively connected to the temperature sensor, and the controller is electrically connected to the second electronic expansion valve 820 and the first electronic expansion valve 810. The controller can acquire and analyze the data of the temperature sensor and the pressure sensor and adjust the opening degrees of the second electronic expansion valve 820 and the first electronic expansion valve 810 according to the analysis results, so as to adjust the temperature or state of the refrigerant, ensure that the refrigerant in the heat transfer component 200 is in a gas-liquid two-phase equilibrium state, and at the same time ensure that all the refrigerant entering the gas compressor 300 is in a gaseous state.

[0073] Specifically, in the heating mode:

[0074] When T1 - Tp2 > Td, the second electronic expansion valve opens wider;

[0075] When T1 - Tp2 < Te, the second electronic expansion valve closes smaller;

[0076] When Te ≤ T1 - Tp2 ≤ Td, the second electronic expansion valve maintains its state,

[0077] wherein, Tp2 is the saturation temperature corresponding to the pressure value P2, Td and Te are predetermined temperature thresholds, and Td > Te.

[0078] In this embodiment, in the cooling mode:

[0079] When T3 - T2 > Ta, the first electronic expansion valve closes smaller;

[0080] When T4 - Tp1 > Tb, the first electronic expansion valve opens wider,

[0081] Otherwise, when T5 - Tp1 > (Tc + db), the first electronic expansion valve opens wider;

[0082] When T5 - Tp1 < (Tc - db), the first electronic expansion valve closes smaller;

[0083] When (Tc - db)°C ≤ T5 - Tp1 ≤ (Tc + db), the first electronic expansion valve maintains its state;

[0084] wherein, Tp1 is the saturation temperature corresponding to the pressure value P1, Ta, Tb, and Tc are predetermined temperature thresholds, and db is an empirical parameter related to the number of control dead zones in the system;

[0085] In this embodiment, the projection of the energy storage component 100 on the heat transfer component 200 is located within the distribution range of the fluid channel 230, so as to ensure that the heat transfer component 200 exchanges heat comprehensively with the energy storage component 100, avoiding local non-heat exchange of the energy storage component 100. In this embodiment, by setting the fluid channel 230, it is possible to ensure that the pressure difference between the first port 210 and the second port 220 is less than a preset value, so that the pressure drop between the first port 210 and the second port 220 is within a preset range. Specifically, the fluid channel 230 includes a plurality of first channels 231 arranged in parallel along the first direction, and second channels 232 connected between the first channels 231.

[0086] See Figure 9 As shown, along the second direction perpendicular to the first direction, the first channels 231 and the second channels 232 are connected to form a plurality of rectangular loops distributed at intervals. The fluid channel 230 includes a third channel 233 connected between the two outermost rectangular loops in the second direction, and the first port 210 is arranged on the third channel 233. Adjacent two rectangular loops are connected by a fourth channel 234, and along the second direction, the fourth channels 234 are alternately distributed on different sides of the rectangular loops along the first direction, and the second port 220 is arranged on the fourth channel 234. In this setting mode, the fluid flows in two different directions at the first port 210 or the second port 220, or converges from two different directions.

[0087] In this embodiment, the heat transfer component 200 includes multiple groups arranged in parallel. A liquid distributor 930 is provided on the first pipe 910 and the second pipe 920. The liquid distributor 930 is used to evenly distribute the refrigerant to multiple groups of heat transfer components 200, so as to be able to heat or cool multiple groups of energy storage components 100 synchronously. In this way, heat can be exchanged with multiple groups of energy storage components 100 at the same time, and the liquid distributor 930 can evenly distribute the refrigerant, so that the temperatures of the branches through which the refrigerant is introduced into each group of heat transfer components 200 are similar, ensuring the same heat exchange effect of multiple groups of heat transfer components 200.

[0088] In other embodiments, multiple groups of heat transfer components 200 are also provided. A plurality of parallel branches 940 arranged in parallel are formed between the first pipe 910 and the second pipe 920. Each parallel branch 940 is provided with a group of heat transfer components 200, and a liquid separation valve 870 for controlling the refrigerant flow rate is provided on each parallel branch 940. In some embodiments, see Figure 7As shown, the liquid separation valve 870 is an electronic expansion valve. A port temperature sensor T6 is also provided on each parallel branch 940. Specifically, a port temperature sensor T6 is provided on each side of the heat transfer component 200. The electronic expansion valve is electrically connected or signal-connected to the port temperature sensor T6. In the cooling mode, the electronic expansion valve adjusts its opening degree according to the value of the port temperature sensor T6 on the side close to the second port 220; in the heating mode, in the cooling mode, the electronic expansion valve adjusts its opening degree according to the value of the port temperature sensor T6 on the side close to the first port 210. In some other embodiments, refer to Figure 8 As shown, the liquid separation valve 870 is a throttler, and the flow rate of the refrigerant in each parallel branch is controlled by the throttler, and the flow rate of the refrigerant flowing into each heat transfer component 200 is controlled.

[0089] Embodiment 2

[0090] Refer to Figure 4 As shown, the main difference between this embodiment and Embodiment 2 is that in this embodiment, the switching between the cooling passage and the heating return passage is not achieved through the first check valve 851, the second check valve 852, the third check valve 853, and the fourth check valve 854. In this embodiment, there are two second electronic expansion valves 820, including a cooling electronic expansion valve 821 and a heating electronic expansion valve 822. The cooling electronic expansion valve 821 is arranged on the pipeline between the first fluid passage 610 of the regenerator 600 and the first pipeline 910, and the heating electronic expansion valve 822 is arranged on the pipeline between the first heat exchanger 510 and the fluid storage tank 700. The thermal management system of the energy storage system includes a fifth check valve 855 that only allows the refrigerant to flow unidirectionally towards the fluid storage tank 700, and a sixth check valve 856 that only allows the refrigerant to flow unidirectionally towards the first fluid passage 610 of the regenerator 600. Among them, the cooling electronic expansion valve 821 is arranged in parallel with the fifth check valve 855, and the heating electronic expansion valve 822 is arranged in parallel with the sixth check valve 856.

[0091] In the cooling mode, in the cooling circulation passage, the sixth check valve 856 is turned on, and the heating electronic expansion valve 822 is fully opened or fully closed. The heating electronic expansion valve 822 serves as a passage that does not limit the refrigerant flow rate, or the heating electronic expansion valve 822 is directly blocked, and it does not play a role in controlling the flow rate. In this mode, the fifth check valve 855 is not turned on, and the refrigerant can only pass through the cooling electronic expansion valve 821, and the cooling electronic expansion valve 821 works normally and plays a role in controlling the flow rate.

[0092] In the heating mode, in the heating cycle path, the fifth one-way valve 855 is conducting, and the cooling electronic expansion valve 821 is fully opened or fully closed. Similarly, the cooling electronic expansion valve 821 serves as a path that does not restrict the refrigerant flow or is directly blocked, and does not play a role in controlling the flow. In this mode, the sixth one-way valve 856 is non-conducting, and the refrigerant can only pass through the heating electronic expansion valve 822, and the heating electronic expansion valve 822 operates normally and plays a role in controlling the flow.

[0093] In this embodiment, a filter is provided on the pipeline between the first fluid path 610 of the recuperator 600 and the first pipeline 910 for filtering the refrigerant to improve the safety of the system.

[0094] Embodiment 3

[0095] See Figure 5 As shown, the difference between this embodiment and Embodiment 3 is that: a plurality of groups of parallel heat transfer components 200 form a heat transfer module. In this embodiment, a plurality of heat transfer modules are arranged in parallel. Specifically, three heat transfer modules are arranged in parallel, further increasing the number of heat management systems for synchronously heating or cooling the energy storage component 100.

[0096] Embodiment 4

[0097] See Figure 6 As shown, the main difference between this embodiment and Embodiment 1 is that: in this embodiment, the heat management system realizes the switching between the cooling cycle path and the heating cycle path through a four-way reversing valve 860. Specifically, the four interfaces of the four-way reversing valve are respectively the first interface a, the second interface b, the third interface c, and the fourth interface d. The outlet of the gas compressor 300 is connected to the first interface a through a pipeline, the first heat exchanger 510 is connected to the second interface b through a pipeline, the second fluid path 620 of the recuperator 600 is connected to the third interface c through a pipeline, and the second heat exchanger 520 is connected to the fourth interface d through a pipeline. In the cooling mode, the first interface a is connected to the second interface b, and the third interface c is connected to the fourth interface d, thereby forming a cooling cycle path. In the heating mode, the first interface a is connected to the fourth interface d, and the second interface b is connected to the third interface c, thereby forming a heating cycle path.

[0098] Embodiment 5

[0099] As Figure 10 As shown, Embodiment 5 of the present utility model provides an energy storage direct cooling / direct heating system, including a refrigeration control system, a heating control system, and a defrosting system, wherein the temperature of the energy storage system is controlled and adjusted through the refrigeration control system and the heating control system, and the frost is removed through the defrosting system.

[0100] As Figure 11As shown in the figure, the process of using the refrigeration control system to cool the energy storage system is as follows: The refrigerant is introduced into the oil separator 2 through the compressor 1. The oil in the refrigerant is separated by the oil separator 2. After flowing through the oil separator 2, the refrigerant enters the outdoor heat exchanger 3, and then enters the liquid receiver 4 through the heating throttle valve 31, and then enters the refrigeration throttle valve 6 through the regenerator 5.

[0101] After passing through the refrigeration throttle valve 6, it enters the refrigeration distributor 61. The refrigeration distributor 61 evenly distributes the refrigerant to each branch cold plate 62 where the energy storage battery is located, and at the same time controls the pressure drop of each refrigerant circuit so that the pressure drop forms a refrigerant temperature change < 0.5°C. Then the refrigerant passes through the heating distributor 7 and returns to the regenerator 8, and then returns to the gas-liquid separator 9 to complete one cycle, and undergoes secondary cycle refrigeration through the compressor 1. In the refrigeration control system, there are also a primary refrigerant circuit, a secondary refrigerant circuit, and a tertiary refrigerant circuit.

[0102] The devices passed by the entire system are as follows:

[0103] Compressor → Oil separator → Outdoor heat exchanger + Outdoor heat exchanger → Heating throttle valve + Check valve → Liquid receiver → Regenerator → Refrigeration throttle valve → Refrigeration distributor → Cold plate → Heating distributor → Refrigeration valve → Regenerator → Gas-liquid separator → Compressor

[0104] Oil circuit: Compressor → Oil separator → Oil return capillary → Suction pipe → Compressor.

[0105] In the refrigeration control system, the heating throttle valve is fully open. The refrigeration throttle valves in the secondary pipeline are automatically controlled according to requirements.

[0106] As Figure 14 shown, the temperature changes evenly at the inlet and outlet of the battery cold plate. This will not cause damage to the battery body due to large temperature changes in the battery that is not in direct contact with the cold plate, thus affecting the service life of the battery. During refrigeration, the throttled refrigerant is distributed through the refrigeration distributor to achieve uniform distribution of the refrigerant flow rate entering each branch of the cold plate.

[0107] As Figure 16 shown, at the same time, the pressure drop at the inlet and outlet of each cold plate is controlled so that the pressure drop forms a refrigerant temperature change < 0.5°C, thereby controlling the saturated evaporation temperature range of the refrigerant inside the cold plate < 0.5°C, ensuring that the maximum temperature difference of each part of the cold plate < 0.5°C. This makes the temperature difference at each point on the contact surface of the battery cells smaller, which is beneficial to the control of the temperature consistency of the battery cells. When measuring the inlet and outlet temperatures of the traditional liquid-cooled cold plate, the temperature difference can reach 2.5°C. Such a large temperature difference is likely to cause chemical changes inside the battery cells, affecting the service life of the battery.

[0108] In the refrigeration control system, the inside of the cold plate is in a two-phase evaporation zone, and the outlet is still in a liquid-carrying state. The temperature inside the cold plate is uniform. After the liquid-carrying gas at the outlet passes through the regenerator, it is in a saturated superheated state, protecting the stable operation of the compressor. At the same time, it exchanges heat with the high-temperature condensed liquid in front of the valve to reduce the liquid temperature.

[0109] As Figure 12 , Figure 15 shown, the specific process of using the heating control system to heat the energy storage system is as follows: The high-temperature and high-pressure superheated refrigerant gas compressed and discharged by the compressor 1 is introduced into the oil separator 2. The oil in the refrigerant is separated by the oil separator 2, and the superheated refrigerant gas flowing through the oil separator 2 enters the outdoor heat exchanger 3 for heat exchange and cooling. Subsequently, it passes through the heating distributor 7 and enters each branch cold plate 62 where the energy storage battery is located, and the degree of subcooling temperature change of the cold plate 62 is controlled to be ≤ 0.5 °C to achieve heating of the energy storage battery on the cold plate 62. Then it enters the refrigeration throttler 6 through the refrigeration distributor 61 until it returns to the regenerator 5. Through the connection between the regenerator 5 and the liquid receiver 4, the refrigerant continues to pass through the liquid receiver 4 and enters the heating throttler 31, and then the refrigerant is heat-exchanged through another group of outdoor heat exchangers 3 (pre-cooled to a saturated state of high-pressure medium-temperature two-phase refrigerant state, so as to ensure that the refrigerant state entering the cold plate is not in a high-temperature state and prevent overheated gas from entering the cold plate and causing the temperature of the battery core to be too high. Specifically, refer to as Figure 15 shown. At this time, the temperature change between the inlet and outlet of the battery cold plate is relatively small), and then it returns to the gas-liquid separator 9 to complete one cycle, and then undergoes a secondary cycle of heating through the compressor 1.

[0110] In the heating mode, through outlet temperature control, the two-phase refrigerant in a saturated state of high-pressure medium-temperature condenses inside the cold plate. At the same time, the refrigerant state leaving the cold plate is still in a two-phase state or has a small degree of subcooling, and the degree of subcooling limit is ≤ 0.5 °C. Thus, the refrigerant is in a two-phase heat exchange state inside the cold plate to achieve the consistency of the refrigerant temperature and make the surface temperature of the cold plate the same. Therefore, the temperature difference at each point of the surface in contact with the battery core is smaller, which is beneficial to the control of the battery core temperature consistency.

[0111] The inside of the cold plate is in a two-phase condensation zone, and the outlet is still in a gas-carrying state. The temperature inside the cold plate is uniform. The gas-carrying liquid at the outlet is further heated by the high-temperature gas coming from the outdoor heat exchanger after passing through the regenerator, forming a superheated refrigerant gas, making the gas in front of the throttle valve in a superheated zone and protecting the stable operation of the unit.

[0112] The devices passed through by the entire system are as follows: compressor → oil separator → outdoor heat exchanger → heating valve → heating distributor → cold plate → refrigeration distributor → refrigeration throttle valve + check valve → regenerator → liquid receiver → heating throttle valve → outdoor heat exchanger → heating valve → regenerator → gas-liquid separator → compressor;

[0113] Oil circuit: compressor → oil separator → oil return capillary → suction pipe → compressor.

[0114] As Figure 13 shown, the energy storage direct cooling / direct heat pump system also includes a defrosting system, and the specific operation is as follows: The oil separator 2 separates oil and gas. The refrigerant enters the outdoor heat exchanger 3, and then enters the liquid receiver 4 through the heating throttle 31. It reflows into the gas-liquid separator 9 through the hot gas defrosting valve 10, and then undergoes secondary cycle defrosting through the compressor 1.

[0115] In the refrigeration control system, the heating control system, and the defrosting system, after being released by the compressor 1, the oil circuit is separated by the oil separator 2, recovered through the oil return capillary 21, and then reflows into the compressor 1 through the suction pipe as a cyclic action.

[0116] In the refrigeration control system, when performing refrigeration operation, the heating pipeline is closed; in the heating control system, when performing heating operation, the refrigeration pipeline is closed. At the same time, this application can also achieve efficiency improvement (reduce intermediate heat exchange).

[0117] Improvement in heat exchange efficiency in the refrigeration mode: The traditional method is: In the liquid cooling heat exchange process: battery cell → cold plate (water-cooled heat exchanger) → secondary coolant → plate heat exchanger (evaporator) → refrigerant.

[0118] As Figure 17 shown, the method adopted by the present utility model is: In the direct cooling heat exchange process: battery cell → cold plate (evaporator) → refrigerant.

[0119] Improvement in heat exchange efficiency in the heating efficiency: The traditional liquid cooling heat exchange process is: battery cell → cold plate (water-cooled heat exchanger) → secondary coolant → plate heat exchanger (evaporator) → refrigerant.

[0120] The method adopted by the present utility model is: In the direct cooling heat exchange process: battery cell → cold plate (evaporator) → refrigerant.

[0121] Moreover, the original liquid cooling PTC electric heating is also cancelled, which further reduces the cost investment of the equipment while improving the efficiency.

[0122] In summary, the beneficial effects of the present utility model:

[0123] 1. When the system of this device is used for refrigeration / heating, multiple outdoor heat exchangers are used for heat exchange operations. Its efficiency is 30% higher than that of a single chiller in terms of thermal efficiency, and energy-saving efficiency is achieved synchronously.

[0124] 2. This device uses a distributor to distribute the refrigerant, achieving more uniform distribution and making the temperature difference between each circuit close. This not only saves energy but also realizes the stable operation of the device system.

[0125] 3. Most of the pipe fittings are used for connection in this device to achieve refrigeration or heating. Therefore, the connection points between components are significantly reduced, and the possibility of refrigerant overflow in the refrigeration or heating process is also reduced, improving the stability of the overall device system operation.

[0126] 4. During the refrigeration process of this device, the cold plate uses two-phase zone heat exchange. The pressure in each branch is the same, the cold plate temperature is the same, and the temperature difference between the inlet and outlet of the cold plate is small. This can limit the deviation of the saturated evaporation temperature in the cold plate to within 0.5°C, making the temperature difference at each point on the contact surface of the battery cell smaller, which is beneficial to the control of the battery cell temperature uniformity.

[0127] 5. This device reduces the configuration of PTC in the system and the use of circulating water pumps, which can reduce cost expenditures.

[0128] 6. The first-stage refrigerant used in this device is distributed to the second-stage refrigerant circuit and regulated by an electronic expansion valve, which can achieve multi-circuit control and the average distribution of refrigerant between circuits, thus realizing the temperature management of multiple clusters of battery packs.

[0129] In summary, the thermal management systems of all the above embodiments can control and manage the temperature of the high-energy-density energy storage box, and can effectively and reliably control the temperature uniformity of the energy storage system. The thermal management system exchanges heat more efficiently by passing the refrigerant into the heat transfer component 200 and directly exchanging heat with the energy storage component 100. The thermal management system includes a cooling circulation path, a heating circulation path, and a defrosting circulation path, with rich functions. By opening and closing the control valve to control the opening and closing of the pipeline, it can drive the conversion of the cooling circulation path, the heating circulation path, and the defrosting circulation path, without the need to additionally set up a heating mechanism or a defrosting mechanism, simplifying the system setup cost. At the same time, the setting of the fluid channel 230 of the heat transfer component 200 can control the magnitude of the pressure difference between the first port 210 and the second port 220, thereby controlling the pressure drop between the first port 210 and the second port 220. When the refrigerant is in a gas-liquid two-phase equilibrium state respectively, the temperature in the fluid channel 230 is uniform, and the heat exchange effect is better.

[0130] The above embodiments are only used to illustrate the technical concept and characteristics of the present utility model. The purpose is to enable those skilled in the art to understand the content of the present utility model and implement it, and it cannot be used to limit the protection scope of the present utility model. Any equivalent changes or modifications made according to the spirit of the present utility model should be covered within the protection scope of the present utility model.

Claims

1. A thermal management system for an energy storage system with a thermal cycle, the energy storage system comprising an energy storage component and a heat transfer component, the heat transfer component having a first port, a second port and a fluid channel connecting the first port and the second port, the first port and the second port being connectable to the thermal management system through a first pipe and a second pipe, the thermal management system comprising a gas compressor, a heat exchanger and a valve assembly, characterized in that: The heat exchanger includes a first heat exchanger and a second heat exchanger which are arranged adjacent to each other. The second heat exchanger has a heat dissipation mechanism for heat exchange between a heat exchange fluid and the surrounding environment. The first heat exchanger has a fan and an air inlet. The heat dissipation mechanism is arranged at the air inlet, and the heat dissipation mechanism is located on the air inlet path of the first heat exchanger.

2. The thermal management system of the energy storage system with thermal cycle according to claim 1, characterized in that: The outlet of the gas compressor, the second heat exchanger, and the second pipeline are connected in sequence through pipelines to form a heating passage for supplying the heat exchange fluid with a preset temperature to the heat transfer component; the first pipeline, the first heat exchanger, and the inlet of the gas compressor are connected in sequence through pipelines to form a heating reflux passage for recovering the heat exchange fluid, the heating passage, the fluid channel in the heat transfer component, and the heating reflux passage constitute a heating circulation passage, and a first electronic expansion valve is provided on the pipeline between the outlet of the gas compressor and the second heat exchanger.

3. The thermal management system of the energy storage system with thermal cycle according to claim 2, characterized in that: The thermal management system also includes a detection control module, which includes a controller, a temperature sensor arranged in a pipeline of the thermal management system and electrically or signal-connected to the controller, the temperature sensor being arranged on a pipeline between the second heat exchanger and the second pipeline, and the controller being configured to acquire data from the temperature sensor and adjust the opening of the first electronic expansion valve according to the acquired data.

4. The thermal management system of the energy storage system with thermal cycle according to claim 3, characterized in that: The pipeline between the outlet of the gas compressor and the second heat exchanger, and the pipeline between the second heat exchanger and the second pipeline are connected through a branch pipeline. The branch pipeline has a first end and a second end respectively arranged at both ends. The first end is connected to the pipeline between the gas compressor and the second heat exchanger, and the second end is connected to the pipeline between the second heat exchanger and the second pipeline. The first electronic expansion valve is arranged on the pipeline between the first end of the branch pipeline and the second heat exchanger, and the temperature sensor is arranged on the pipeline between the second end of the branch pipeline and the second pipeline.

5. The thermal management system of the energy storage system with thermal cycle according to claim 2, characterized in that: The thermal management system also includes a detection control module, which includes a controller and a pressure sensor arranged in a pipeline of the thermal management system and electrically or signal-connected to the controller. The pressure sensor includes a first pressure sensor arranged at the inlet of the gas compressor and a second pressure sensor arranged at the outlet of the gas compressor. The controller is electrically or communicatively connected to the gas compressor, and the controller is configured to adjust the rotation speed of the gas compressor according to the detection value of the pressure sensor. The controller is also electrically or communicatively connected to the valve assembly, and the controller is configured to control the opening and closing and / or opening degree of the valve according to a preset program.

6. The thermal management system of the energy storage system with thermal cycle according to claim 5, characterized in that: The valve assembly includes a first solenoid valve arranged on the pipeline between the outlet of the gas compressor and the second heat exchanger, and a second solenoid valve arranged on the pipeline between the inlet of the compressor and the first heat exchanger. When the first solenoid valve and the second solenoid valve are opened, the heating circulation passage is opened.

7. The thermal management system of the energy storage system with thermal cycle according to claim 1, characterized in that: The thermal management system further includes the heat exchange fluid; and / or the heat exchange fluid is a refrigerant or a fluid other than a refrigerant.

8. The thermal management system of the energy storage system with thermal cycle according to claim 1, characterized in that: The heat exchange fluid is refrigerant R134a, refrigerant R1234yf, refrigerant R410A, refrigerant R513A, refrigerant R513B or refrigerant R454B.

9. The thermal management system of the energy storage system with thermal cycle according to claim 1, characterized in that: The first heat exchanger also has a heat exchange chamber, an air outlet and a heat exchange mechanism. The air inlet and the air outlet are connected to the heat exchange chamber. The fan is arranged at the air outlet. The heat exchange mechanism is located in the heat exchange chamber, and the heat exchange mechanism is connected to the gas compressor through a pipeline. The heat exchange mechanism is configured to allow the heat exchange fluid passing therein to exchange heat in the heat exchange chamber.

10. The thermal management system of the energy storage system with thermal cycle according to claim 1, characterized in that: The heat exchange fluid in the fluid channel is in a gas-liquid two-phase equilibrium state; and / or, the thermal management system also includes a fluid storage tank and a regenerator, the outlet of the gas compressor, the first heat exchanger, the fluid storage tank, the regenerator, and the first pipeline are connected in sequence through pipelines to form a cooling passage for supplying a heat exchange fluid with a preset temperature to the heat transfer component, wherein a first electronic expansion valve is provided on the pipeline between the first fluid passage of the regenerator and the first pipeline; the second pipeline, the regenerator, and the inlet of the gas compressor are connected in sequence through pipelines to form a cooling reflux passage for recovering the heat exchange fluid, and the cooling passage, the fluid channel in the heat transfer component, and the cooling reflux passage constitute a cooling circulation passage.

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