A thermal management system and energy storage container

Abstract

The application provides a heat management system and an energy storage container. The heat management system is used for heat exchange of a battery in an energy storage system and comprises a refrigerant circulation loop. The refrigerant circulation loop is provided with a compressor, a first heat exchanger, a second heat exchanger and a third heat exchanger which are connected with each other. The third heat exchanger has a first heat exchange part and a second heat exchange part. An outlet of the compressor is connected with a pressure regulating valve, the first heat exchange part and a first port of the second heat exchanger through pipelines in sequence. A second port of the second heat exchanger is connected with the first heat exchanger, the second heat exchange part and an inlet of the compressor through pipelines in sequence, so that the refrigerant flowing out of the compressor in a heating mode is subjected to pressure regulation and temperature reduction regulation and then flows into the second heat exchanger. Through heat exchange between the refrigerant and the battery, the heat exchange efficiency of the battery is improved. Meanwhile, the superheat degree of the refrigerant is eliminated and the supercooling degree is reduced before heat exchange, so that the heat exchange uniformity is improved and the temperature uniformity of the battery is improved.

Description

Technical Field

[0001] This application relates to the field of thermal management technology for batteries in energy storage systems, and specifically to a thermal management system and an energy storage container including the thermal management system. Background Technology

[0002] An energy storage system is a system that converts other energy sources, such as solar energy, into electrical energy and stores it through energy storage devices. It combines energy generation technology and energy storage technology and is widely used in various scenarios such as residential, commercial, and industrial applications. The core of an energy storage system consists of solar panels, batteries, inverters, and other auxiliary equipment. Battery temperature control is a critical factor in ensuring the normal operation of the system and requires high temperature control accuracy.

[0003] In the process of realizing this invention, the inventors discovered at least the following technical problems in the prior art: In the prior art, battery temperature control generally adopts liquid cooling, using a liquid (such as water or a special coolant) as a heat transfer medium to remove heat from the battery through a circulating cooling system. However, this method has slow heat exchange efficiency and a large temperature difference between the inlet and outlet of the heat exchange plate, making it difficult to heat the battery evenly; and uneven battery temperature will seriously affect the battery's use and lifespan. Summary of the Invention

[0004] In view of this, this application aims to provide a thermal management system that improves the heat exchange efficiency of the battery by exchanging heat between the refrigerant and the battery. At the same time, it eliminates the superheat of the refrigerant and reduces the supercooling before heat exchange to improve the heat exchange uniformity and the temperature uniformity of the battery. This at least partially improves the problem of uneven battery temperature caused by large temperature differences in the heat exchanger, which affects the use and life of the battery.

[0005] This application provides a thermal management system for heat exchange of batteries in an energy storage system, including a refrigerant circulation loop. The refrigerant circulation loop is provided with a compressor, a first heat exchanger that exchanges heat with the environment, a second heat exchanger that exchanges heat with the battery, and a third heat exchanger that are interconnected. The third heat exchanger has a first heat exchange section and a second heat exchange section that exchanges heat with the first heat exchange section.

[0006] The compressor outlet is connected in sequence to the pressure regulating valve, the first heat exchange section, and the first port of the second heat exchanger via pipelines. The second port of the second heat exchanger is connected in sequence to the first heat exchanger, the second heat exchange section, and the compressor inlet via pipelines, so that the refrigerant flowing out of the compressor in heating mode is regulated by pressure and temperature before flowing into the second heat exchanger.

[0007] In one possible implementation, the second heat exchanger is a direct cooling plate that directly contacts the battery for heat exchange.

[0008] In one possible implementation, a pressure sensor and / or a temperature sensor are provided at both ports of the second heat exchanger, and the controller adjusts the opening of the pressure regulating valve according to the pressure sensor and / or temperature sensor to reduce the temperature difference between the two ports of the second heat exchanger.

[0009] In one possible implementation, the first port of the first heat exchange section is connected to the outlet of the compressor via a first branch and to the inlet of the compressor via a second branch arranged in parallel with the first branch. The pressure regulating valve is provided on the first branch and the check valve is provided on the second branch. The second port of the first heat exchange section is connected to the first port of the second heat exchanger via a first main line.

[0010] In one possible implementation, the first port of the first heat exchanger is connected to the compressor and the second port of the second heat exchanger respectively through parallel pipelines, and the second port is connected to the first port of the second heat exchange section through a third main pipeline. The second port of the second heat exchange section is connected to the compressor and the second port of the second heat exchanger respectively through parallel pipelines.

[0011] In one possible implementation, a fourth main circuit is also provided, which is connected to the compressor inlet in cooling mode and to the compressor outlet in heating mode.

[0012] The second port of the second heat exchanger is provided with a second main circuit;

[0013] The first port of the first heat exchanger is connected to the second main line via the third branch and to the fourth main line via the sixth branch connected in parallel with the third branch; the second port of the second heat exchange section is connected to the second main line via the fourth branch and to the fourth main line via the fifth branch.

[0014] One-way valves are provided on the third branch, the fourth branch, the fifth branch and the sixth branch.

[0015] In one possible implementation, a multi-way valve is also included. The compressor outlet is provided with a return main line and the inlet is provided with an outflow main line. The first valve port of the multi-way valve is connected to the outflow main line, the second valve port is connected to the pipeline connecting the first port of the first heat exchange section, the third valve port is connected to the return main line, and the fourth valve port is connected to the fourth main line.

[0016] In cooling mode, the fourth valve port is connected to the first valve port, and the third valve port is connected to the second valve port; in heating mode, the first valve port is connected to the second valve port, and the third valve port is connected to the fourth valve port.

[0017] In one possible implementation, the second heat exchanger has multiple units arranged in parallel, and a staged throttling component is provided between the second heat exchanger and the first heat exchanger. The staged throttling component can throttle the refrigerant flowing out of the first heat exchanger at least twice and make the throttled refrigerant flow evenly to the multiple units of the second heat exchanger arranged in parallel.

[0018] In one possible implementation, the graded throttling assembly includes a first throttling valve, a first distributor, and a second throttling valve.

[0019] The second throttle valve is configured one-to-one with the second heat exchanger and is connected to the first distributor. The first throttle valve is connected between the first heat exchanger and the first distributor.

[0020] This application also provides an energy storage container, including a thermal management system as described in any of the preceding claims.

[0021] This application also provides a control method for a thermal management system, applicable to the thermal management system described in any of the preceding claims, comprising the following steps:

[0022] Determine if it is in heating mode.

[0023] If so, open the pressure regulating valve to allow the refrigerant flowing from the compressor to flow into the pressure regulating valve, and then flow into the second heat exchanger after passing through the pressure regulating valve and the first heat exchange section of the third heat exchanger in sequence.

[0024] In one possible implementation, the following steps are also included:

[0025] The pressure and / or temperature values ​​at the two ports of the second heat exchanger are detected. If the detection results exceed the preset range, the opening of the pressure regulating valve is adjusted according to the detection results to reduce the temperature difference between the two ports of the second heat exchanger.

[0026] The thermal management system provided in this application is used for heat exchange of batteries in an energy storage system. It uses a second heat exchanger to exchange heat with refrigerant circulated by a compressor, achieving high heat exchange efficiency. Simultaneously, in heating mode, the refrigerant flowing from the compressor first undergoes pressure regulation, such as reducing the pressure to minimize its supercooling, and then passes through a third heat exchanger for cooling to eliminate superheat. The refrigerant then flows back into the second heat exchanger. This eliminates and minimizes refrigerant superheat, allowing the refrigerant to enter the second heat exchanger in a two-phase state and transfer heat to the battery within the two-phase state. This reduces the temperature difference between the inlet and outlet of the second heat exchanger, improves the temperature uniformity of various areas on the surface of the second heat exchanger, and enhances the temperature uniformity of various areas when the battery absorbs heat. This at least partially solves the problem of uneven battery temperature caused by large temperature differences in the heat exchanger, which affects battery use and lifespan. Attached Figure Description

[0027] Figure 1 The diagram shown is a schematic representation of the thermal management system in an embodiment of this application.

[0028] Figure 2 The diagram shown is a schematic representation of the refrigerant flow path in the heating mode of this application embodiment;

[0029] Figure 3 The diagram shown is a schematic representation of the refrigerant flow path in the refrigeration mode of this application embodiment.

[0030] Figures 1-3 :

[0031] 1. Compressor; 2. Pressure regulating valve; 3. Third heat exchanger; 4. Second heat exchanger; 5. First heat exchanger; 6. Multi-way valve; 7. Outflow main line; 8. Return main line; 9. First branch line; 10. Second branch line; 101. First check valve; 11. First main line; 12. Direct cooling branch line; 13. Second main line; 14. Third branch line; 141. Second check valve; 15. Sixth branch line; 151. Fifth check valve; 16. Fourth main line; 17. Third main line; 18. Fourth branch line; 181. Third check valve; 19. Fifth branch line; 191. Fourth check valve; 20. Pressure sensor; 21. First throttle valve; 22. First distributor; 23. Second throttle valve; 24. Second distributor; 25. Liquid receiver; 26. Filter. Detailed Implementation

[0032] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0033] Please refer to the attached document. Figure 1-3 This application provides a thermal management system suitable for energy storage systems, used for heat exchange of multiple batteries in the energy storage system. The thermal management system includes a refrigerant circulation loop, which is equipped with an interconnected compressor 1, a first heat exchanger 5 for heat exchange with the environment, a second heat exchanger 4 for heat exchange with the batteries, and a third heat exchanger 3. The third heat exchanger 3 has a first heat exchange section and a second heat exchange section for heat exchange with the first heat exchange section.

[0034] The outlet of compressor 1 is connected in sequence to pressure regulating valve 2, the first heat exchange section, and the first port of the second heat exchanger 4 via pipelines. The second port of the second heat exchanger 4 is connected in sequence to the first heat exchanger 5, the second heat exchange section, and the inlet of compressor 1 via pipelines. The second heat exchanger 4 uses refrigerant regulated by compressor 1 to cool or heat the battery. Specifically, the second heat exchanger 4 can be a direct-cooling plate, which directly contacts the battery, for example, by being attached to the bottom of the battery for heat exchange.

[0035] Meanwhile, in heating mode, the refrigerant flowing out of compressor 1 flows into the second heat exchanger 4 after pressure and temperature regulation.

[0036] In heating mode, the refrigerant flows out of compressor 1 at high temperature and high pressure. Because the second heat exchanger 4 has high heat exchange efficiency, if the refrigerant has a high superheat (i.e., enters the second heat exchanger 4 as a highly superheated gaseous state), it will condense rapidly within the second heat exchanger 4. This results in a large temperature difference between the inlet and outlet ports of the second heat exchanger 4, meaning a large temperature difference between different areas of the second heat exchanger 4. Consequently, the heat exchange of energy storage components absorbing heat from the second heat exchanger 4, such as batteries, will be uneven, leading to uneven temperatures across different areas of the battery and affecting its operation and lifespan. Similarly, if the refrigerant has a high subcooling, it will also result in a large temperature difference between different areas of the second heat exchanger 4, leading to uneven temperatures across different areas of the battery.

[0037] Based on this, in this application, a pressure regulating valve 2 and a third heat exchanger 3 are sequentially installed on the pipeline from the outlet of compressor 1 to the second heat exchanger 4. The pressure regulating valve 2 is used to regulate the pressure of the refrigerant flowing out of compressor 1 and change the state of the refrigerant (isenthalpic pressure and temperature reduction process). In this way, the supercooling and superheat of the refrigerant can be reduced, the superheat of the refrigerant at the inlet of the second heat exchanger 4 can be reduced, and the supercooling of the refrigerant at the outlet of the second heat exchanger 4 can be reduced. The third heat exchanger 3 is used to transfer the heat from the refrigerant after pressure regulation to the refrigerant returning to compressor 1, further reducing the temperature of the refrigerant and changing the phase state of the refrigerant, eliminating the superheat of the refrigerant, so that the refrigerant enters the second heat exchanger 4 in a two-phase state and transfers heat to the battery in a two-phase state in the second heat exchanger 4, thereby reducing the temperature difference between the inlet and outlet ports of the second heat exchanger 4, improving the temperature uniformity of each area on the surface of the second heat exchanger 4, and improving the temperature uniformity of each area when the battery absorbs heat.

[0038] As can be seen, the thermal management system provided in this application uses refrigerant circulated by compressor 1 to exchange heat with the battery through the second heat exchanger 4. At the same time, in the heating mode, the refrigerant flowing out of compressor 1 is first reduced by pressure regulation to reduce subcooling and then reduced by temperature regulation to eliminate superheat. After that, the refrigerant flows into the second heat exchanger 4, so that the refrigerant enters the second heat exchanger 4 in a two-phase state and transfers heat to the battery in the second heat exchanger 4 in a two-phase state. This improves the heat exchange uniformity and the battery temperature uniformity, and at least to a certain extent solves the problem of uneven battery temperature caused by large temperature differences in the heat exchanger, which affects the use and life of the battery.

[0039] The pressure regulating valve 2 can specifically be an electronic expansion valve. The opening degree of the pressure regulating valve 2 can be adjusted based on the temperature difference and / or pressure difference at the two ports of the second heat exchanger 4. For example, if a pressure sensor 20 and / or a temperature sensor are installed at both ports of the second heat exchanger 4, the controller adjusts the opening degree of the pressure regulating valve 2 based on the pressure sensor 20 and / or the temperature sensor to reduce the temperature difference at the two ports of the second heat exchanger 4, for example, to make the temperature difference ≤ 0.5℃. This ensures that the temperature difference between the refrigerant entering and exiting the second heat exchanger 4 is not too large, guaranteeing temperature uniformity in all areas of the battery.

[0040] For example, the first port of the first heat exchange section is connected to the outlet of the compressor 1 via a first branch 9, and to the inlet of the compressor 1 via a second branch 10 arranged in parallel with the first branch 9. A pressure regulating valve 2 is installed on the first branch 9, and a one-way valve, referred to as the first one-way valve 101, is installed on the second branch 10. The first one-way valve 101 guides the flow from the third heat exchanger 3 to the compressor 1 through the second branch 10. The second port of the first heat exchange section is connected to the first port of the second heat exchanger 4 via a first main line 11. In heating mode, the refrigerant enters the first branch 9, flows through the pressure regulating valve 2, enters the third heat exchanger 3, and then flows into the second heat exchanger 4 to exchange heat with the battery. In cooling mode, the refrigerant flows out of the second heat exchanger 4, flows through the third heat exchanger 3, and then flows back to the compressor 1 via the second branch 10. In this way, the pipeline structure is simple, which can reduce manufacturing and maintenance costs and is easy to maintain; the maintainability of the thermal management system is also an important factor affecting the stability of system operation.

[0041] In some embodiments, the first port of the first heat exchanger 5 is connected to the second ports of the compressor 1 and the second heat exchanger 4 via parallel pipes, and the second port is connected to the first port of the second heat exchange section of the third heat exchanger 3 via a third main line 17. The second port of the second heat exchange section is connected to the second ports of the compressor 1 and the second heat exchanger 4 via parallel pipes. With this configuration, the inlet and outlet of the first heat exchanger 5 and the inlet and outlet of the second heat exchange section of the third heat exchanger 3 remain unchanged in both cooling and heating modes. The flow direction of the refrigerant in the first heat exchanger 5 and the second heat exchange section of the third heat exchanger 3 is consistent in both cooling and heating modes, significantly simplifying the piping structure.

[0042] Specifically, such as Figure 1 As shown, the system also includes a fourth main line 16, which is connected to the inlet of compressor 1 in cooling mode and to the outlet of compressor 1 in heating mode. A second main line 13 is provided at the second port of the second heat exchanger 4.

[0043] The first port of the first heat exchanger 5 is connected to the second main line 13 via the third branch 14 and to the fourth main line 16 via the sixth branch 15, which is in parallel with the third branch 14. Both the third branch 14 and the sixth branch 15 are equipped with check valves. The check valve on the third branch 14 is designated as the second check valve 141, which directs the flow from the second main line 13 to the first heat exchanger 5 through the third branch 14. The check valve on the sixth branch 15 is designated as the fifth check valve 151, which directs the flow from the compressor 1 outlet to the first heat exchanger 5 through the sixth branch 15.

[0044] The second port of the second heat exchange section is connected to the second main line 13 via the fourth branch 18 and to the fourth main line 16 via the fifth branch 19. Both the fourth branch 18 and the fifth branch 19 are equipped with check valves. The check valve on the fourth branch 18 is designated as the third check valve 181, which directs the flow from the third heat exchanger 3 to the second main line 13 (i.e., the second heat exchanger 4) through the fourth branch 18. The check valve on the fifth branch 19 is designated as the fourth check valve 191, which directs the flow from the third heat exchanger 3 to the inlet of the compressor 1 through the fifth branch 19. This configuration ensures flow direction through check valves and shares most of the piping, resulting in a simple overall piping system structure with fewer pipes and valves while maintaining heat exchange functionality.

[0045] In a further embodiment, the system also includes a multi-way valve 6. The compressor 1 has a return main line 8 at its outlet and an outflow main line 7 at its inlet. The first valve port of the multi-way valve 6 is connected to the outflow main line 7, the second valve port is connected to the first branch line 9 and the second branch line 10, the third valve port is connected to the return main line 8, and the fourth valve port is connected to the fourth main line 16. In cooling mode, the fourth valve port is connected to the first valve port, the fourth main line 16 is connected to the outflow main line 7, the third valve port is connected to the second valve port, and the third heat exchanger 3 is connected to the return main line 8. In heating mode, the first valve port is connected to the second valve port, the third heat exchanger 3 is connected to the outflow main line 7, the third valve port is connected to the fourth valve port, and the fourth main line 16 is connected to the return main line 8.

[0046] In cooling mode, the refrigerant circulation loop is as follows: compressor 1 outlet - outflow main line 7 - fourth main line 16 - sixth branch line 15 - first heat exchanger 5 - third main line 17 - second heat exchange section of third heat exchanger 3 - fourth branch line 18 - second main line 13 - second heat exchanger 4 - first main line 11 - first heat exchange section of third heat exchanger 3 - second branch line 10 - return main line 8 - compressor 1 inlet.

[0047] In heating mode, the refrigerant circulation loop is as follows: compressor 1 outlet - outflow main line 7 - first branch line 9 - first heat exchange section of third heat exchanger 3 - first main line 11 - second heat exchanger 4 - second main line 13 - third branch line 14 - first heat exchanger 5 - third main line 17 - second heat exchange section of third heat exchanger 3 - fifth branch line 19 - fourth main line 16 - return main line 8 - compressor 1 inlet.

[0048] This configuration ensures flow direction via a one-way valve and switches connectivity via a multi-way valve 6. Only two short parallel pipes are needed at the inlet of the first heat exchanger 5, the first port of the first heat exchange section of the third heat exchanger 3, and the outlet of the second heat exchange section of the third heat exchanger 3. In both cooling and heating modes, the remaining pipes can be shared. The entire thermal management system, while ensuring heat exchange functionality, has a simple piping system structure, uses fewer pipes and valves, significantly simplifies piping composition, reduces costs, and lowers the difficulty of pipe maintenance. At the same time, the simple piping structure and fewer components result in a lower overall component failure frequency, reducing the probability of damage and improving durability and safety.

[0049] The multi-way valve 6 can be a four-way valve, or of course, a five-way valve or a six-way valve, etc.

[0050] Typically, there are multiple second heat exchangers 4 arranged in parallel. Each second heat exchanger 4 is installed on a direct cooling branch 12. Each direct cooling branch 12 is connected to the first main branch 11 at one end and to the second main branch 13 at the other end.

[0051] To ensure uniform flow of the refrigerant in each of the second heat exchangers 4 under cooling mode and thus ensure uniform temperature of the battery, in some embodiments, a graded throttling component is provided between the second heat exchanger 4 and the first heat exchanger 5. The graded throttling component can throttle the refrigerant flowing out of the first heat exchanger 5 at least twice and make the throttled refrigerant flow evenly to the multiple second heat exchangers 4 arranged in parallel.

[0052] First, compressor 1 compresses the refrigerant into a high-temperature, high-pressure refrigerant, which flows to the first heat exchanger 5. At this point, the first heat exchanger 5 acts as a condenser, where the high-temperature, high-pressure refrigerant exchanges heat with the external environment, transforming into a medium-temperature, high-pressure refrigerant. Next, the medium-temperature, high-pressure refrigerant flowing from the first heat exchanger 5 flows to a staged throttling assembly, which throttles the medium-temperature, high-pressure refrigerant into a low-temperature, low-pressure refrigerant, which flows to the second heat exchanger 4. The low-temperature, low-pressure refrigerant flowing through the second heat exchanger 4 exchanges heat with the battery, transferring the cooling energy from the refrigerant to the battery. Then, the refrigerant flowing from the second heat exchanger 4, with its temperature increased, flows to a gas-liquid separator, which separates the gas and liquid components in the refrigerant. The gaseous refrigerant flows back to compressor 1, thus completing one cooling cycle for the battery.

[0053] By setting up a graded throttling component, the refrigerant flowing through the first heat exchanger 5 can be throttled at least twice. On the one hand, the flow rate of the refrigerant flowing into each second heat exchanger 4 can be adjusted so that the flow rate and temperature of the refrigerant flowing through each second heat exchanger 4 are basically the same, thereby improving the temperature uniformity of each battery. On the other hand, the temperature of the refrigerant can be further reduced through the two throttling processes, thereby improving the cooling efficiency of the second heat exchanger 4 and the thermal storage battery.

[0054] This configuration enables the uniform distribution of the refrigerant in multiple batteries after throttling in cooling mode, thus allowing multiple batteries to be cooled evenly and precisely.

[0055] It should be noted that each second heat exchanger 4 exchanges heat with the same number of batteries. For example, the second heat exchanger 4 is set up one-to-one with the batteries, or the second heat exchanger 4 is set up one-to-many with the batteries. That is to say, each second heat exchanger 4 needs to cool or heat the same number of batteries.

[0056] Specifically, the graded throttling assembly includes a first throttling valve 21, a first distributor 22, and a second throttling valve 23. The second throttling valve 23 is configured one-to-one with the second heat exchanger 4 and is connected to the first distributor 22. Specifically, the second throttling valve 23 is installed on each direct cooling branch 12, and one second throttling valve 23 is installed on each direct cooling branch 12. The first distributor 22 is connected to the second main line 13. The first throttling valve 21 is connected between the first heat exchanger 5 and the first distributor 22 and is also installed on the second main line 13. The first distributor 22 is connected to the first throttling valve 21 and has multiple first branch interfaces. The multiple first branch interfaces are respectively connected to multiple second heat exchangers 4 connected in parallel, that is, the multiple first branch interfaces are connected one-to-one with multiple direct cooling branches 12.

[0057] The first throttle valve 21 and the second throttle valve 23 can be one of an electronic expansion valve, a throttle valve, or a capillary tube. Preferably, the first throttle valve 21 is an electronic expansion valve, which has the function of regulating refrigerant pressure. Thus, after the medium-temperature, high-pressure refrigerant flows to the first throttling valve 21, the first throttling valve 21 throttles and regulates the pressure of the medium-temperature, high-pressure refrigerant, changing it into a low-temperature, low-pressure refrigerant. This allows the refrigerant to enter the first distributor 22 in a suitable phase. Then, it flows through multiple first branch ports of the first distributor 22 to multiple parallel-connected second heat exchangers 4. Since a second throttling valve 23 is installed on the inlet side of each second heat exchanger 4 (in the cooling mode), by adjusting the opening of the second throttling valve 23 on the inlet side of each second heat exchanger 4, the refrigerant flowing out of the first distributor 22 can flow evenly to the multiple parallel-connected second heat exchangers 4, ensuring that each second heat exchanger 4 receives the same flow rate. The refrigerant flowing through each second heat exchanger 4 then exchanges heat with the corresponding battery, transferring approximately the same amount of cooling energy to each battery. Furthermore, since the first throttling valve 21 is an electronic expansion valve, it regulates the refrigerant pressure, ensuring the refrigerant enters each second heat exchanger 4 in a suitable phase, thus improving heat exchange uniformity.

[0058] The second throttle valve 23 can be a mechanical valve. That is, the opening of the second throttle valve 23 can be adjusted manually by the operator. Since the second heat exchanger 4 and the second throttle valve 23 are located on the customer side, i.e., in the area where the battery is located, while the compressor 1, the first heat exchanger 5, and the first valve and other electronic components are all located on the unit side, setting the second throttle valve 23 as a mechanical valve avoids the need for control components on the customer side. This simplifies the overall control system of the thermal management system and reduces the probability of malfunctions during operation.

[0059] A second distributor 24 is also provided at another port of the second heat exchanger 4, and the second distributor 24 is located on the first main line 11. In the cooling mode, the refrigerant flowing out from each of the inner heat exchangers is collected by the second distributor 24 and flows back to the compressor 1; in the heating mode, the refrigerant is evenly distributed to each of the second heat exchangers 4 by the second distributor 24.

[0060] In some embodiments, a receiver 25 and a filter 26 are provided between the first heat exchanger 5 and the staged throttling assembly; alternatively, a first distributor 22 is provided on the second main circuit 13, and a receiver 25 and a filter 26 are provided between the first heat exchanger 5 and the first distributor 22. Specifically, the receiver 25 is used to store refrigerant to ensure that the system can adjust and stabilize the refrigerant circulation volume when operating conditions change. When the system needs to increase the refrigerant supply, the receiver 25 can provide sufficient refrigerant; when the system needs to reduce the refrigerant supply, the receiver 25 can store excess refrigerant. The filter 26 is used to filter impurities in the refrigerant and protect the compressor 1: the filter 26 filters impurities and particles in the refrigerant, preventing these impurities from entering the compressor 1, thereby avoiding the compressor 1 from malfunctioning due to impurities clogging or damage, and avoiding sudden impacts between liquid refrigerant and circuit oil, thereby protecting the electric air conditioning compressor 1 from damage, ensuring the normal operation of the thermal management system and the long-term stable use of the equipment.

[0061] Embodiments of this application also provide an energy storage container, including the thermal management system described above. Since the energy storage container includes the aforementioned thermal management system, the beneficial effects of the thermal management system on the energy storage container are as described above and will not be repeated here.

[0062] This application also provides a control method for a thermal management system, applicable to the thermal management system described in any of the above embodiments, comprising the following steps:

[0063] Determine if it is in heating mode.

[0064] If so, open the pressure regulating valve 2 so that the refrigerant flowing out of the compressor 1 flows into the pressure regulating valve 2, and then flows into the second heat exchanger 4 after passing through the pressure regulating valve 2 and the first heat exchange section of the third heat exchanger in sequence; that is, the refrigerant flowing out of the compressor 1 first flows into the pressure regulating valve 2, flows out of the pressure regulating valve 2 and then flows into the first heat exchange section of the third heat exchanger 3, and then flows into the second heat exchanger 4 from the first heat exchange section.

[0065] Furthermore, the control method for the thermal management system also includes the following steps:

[0066] The pressure and / or temperature values ​​at the two ports of the second heat exchanger 4 are detected. If the detection results exceed the preset range, the opening of the pressure regulating valve 2 is adjusted according to the detection results to reduce the temperature difference between the two ports of the second heat exchanger 4. For example, in step 1, the preset range is set to a temperature difference of 0.5 degrees Celsius; in step 2, the temperature values ​​at the two ports of the second heat exchanger 4 are detected; in step 3, if the detection results exceed the preset range, the opening of the pressure regulating valve 2 is increased; if the detection results are within the preset range, the process returns to step 2.

[0067] Specifically, it may also include the following steps:

[0068] In heating mode, the first and second valve ports of the multi-way valve 6 are connected, as are the third and fourth valve ports. The pressure regulating valve 2 and the first throttle valve 21 are opened, and the compressor 1 is started. The refrigerant discharged from the compressor 1 flows sequentially through the first and second valve ports of the multi-way valve 6, the pressure regulating valve 2, the first heat exchange section of the third heat exchanger 3, the second heat exchanger 4, the first throttle valve 21, the first heat exchanger 5, the second heat exchange section of the third heat exchanger 3, the third and fourth valve ports of the multi-way valve 6, and then flows back to the compressor 1.

[0069] In cooling mode, the first and fourth valve ports of the multi-way valve 6 are connected, as are the second and third valve ports. The pressure regulating valve 2 is closed, the first throttle valve 21 is opened, and the compressor 1 is started. The refrigerant discharged from the compressor 1 flows sequentially through the first and fourth valve ports of the multi-way valve 6, the first heat exchanger 5, the second heat exchange section of the third heat exchanger 3, the first throttle valve 21, the second heat exchanger 4, the first heat exchange section of the third heat exchanger 3, the second and third valve ports of the multi-way valve 6, and then flows back to the compressor 1.

[0070] The basic principles of this application have been described above with reference to specific embodiments. However, it should be noted that the advantages, benefits, and effects mentioned in this application are merely examples and not limitations, and should not be considered as essential features of each embodiment of this application. Furthermore, the specific details disclosed above are for illustrative and facilitative purposes only, and are not limitations. These details do not limit the application to the necessity of employing the aforementioned specific details for implementation.

[0071] The components and devices described in this application are merely illustrative examples and are not intended to require or imply that they must be connected, arranged, or configured in the manner shown in the accompanying drawings. As those skilled in the art will recognize, these components and devices can be connected, arranged, and configured in any manner. Words such as “comprising,” “including,” “having,” etc., are open-ended terms meaning “including but not limited to,” and are used interchangeably with them. The terms “or” and “and” as used herein refer to the words “and / or,” and are used interchangeably with them unless the context clearly indicates otherwise. The term “such as” as used herein refers to the phrase “such as but not limited to,” and is used interchangeably with it.

[0072] It should also be noted that in the apparatus and equipment of this application, the components can be disassembled and / or reassembled. These disassemblies and / or reassemblies should be considered as equivalent solutions of this application.

[0073] The above description of the disclosed aspects is provided to enable any person skilled in the art to make or use this application. Various modifications to these aspects will be readily apparent to those skilled in the art, and the general principles defined herein can be applied to other aspects without departing from the scope of this application. Therefore, this application is not intended to be limited to the aspects shown herein, but rather to be accorded the widest scope consistent with the principles and novel features disclosed herein.

[0074] The above description has been given for purposes of illustration and description. Furthermore, this description is not intended to limit the embodiments of this application to the forms disclosed herein. Although numerous exemplary aspects and embodiments have been discussed above, those skilled in the art will recognize certain variations, modifications, alterations, additions, and sub-combinations thereof.

[0075] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications or equivalent substitutions made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A thermal management system, characterized in that, Used for heat exchange of multiple batteries in an energy storage system, including a refrigerant circulation loop, wherein the refrigerant circulation loop is provided with a compressor (1) connected to each other, a first heat exchanger (5) that exchanges heat with the environment, a second heat exchanger (4) that exchanges heat with the batteries, and a third heat exchanger (3), wherein the third heat exchanger (3) has a first heat exchange section and a second heat exchange section that exchanges heat with the first heat exchange section. The outlet of the compressor (1) is connected in sequence to the first port of the pressure regulating valve (2), the first heat exchange section and the second heat exchanger (4) via pipelines. The second port of the second heat exchanger (4) is connected in sequence to the first heat exchanger (5), the second heat exchange section and the inlet of the compressor (1) via pipelines, so that the refrigerant flowing out of the compressor (1) in the heating mode flows into the second heat exchanger (4) after the pressure is regulated by the pressure regulating valve and the temperature is regulated by the third heat exchanger. The second heat exchanger (4) has multiple units arranged in parallel. A graded throttling component is provided between the second heat exchanger (4) and the first heat exchanger (5). In the cooling mode, the graded throttling component can throttle the refrigerant flowing out of the first heat exchanger (5) at least twice and make the throttled refrigerant flow evenly to the multiple units of the second heat exchanger (4) arranged in parallel. The graded throttling assembly includes a first throttling valve (21), a first distributor (22), and a second throttling valve (23). The second throttle valve (23) is set one-to-one with the second heat exchanger (4) and both are connected to the first distributor (22). The first throttle valve (21) is connected between the first heat exchanger (5) and the first distributor (22).

2. The thermal management system as described in claim 1, characterized in that, The second heat exchanger (4) is a direct cooling plate, which is in direct contact with the battery for heat exchange.

3. The thermal management system as described in claim 1, characterized in that, Pressure sensors (20) and / or temperature sensors are provided at both ports of the second heat exchanger (4). The controller adjusts the opening of the pressure regulating valve (2) according to the pressure sensors (20) and / or temperature sensors to reduce the temperature difference between the two ports of the second heat exchanger (4).

4. The thermal management system as described in claim 1, characterized in that, The first port of the first heat exchange section is connected to the outlet of the compressor (1) through the first branch (9) and to the inlet of the compressor (1) through the second branch (10) which is arranged in parallel with the first branch (9). The pressure regulating valve (2) is provided on the first branch (9) and the check valve is provided on the second branch (10). The second port of the first heat exchange section is connected to the first port of the second heat exchanger (4) through the first main line (11).

5. The thermal management system as described in claim 1, characterized in that, The first port of the first heat exchanger (5) is connected to the second port of the compressor (1) and the second heat exchanger (4) respectively through parallel pipelines. The second port is connected to the first port of the second heat exchange section through the third main line (17). The second port of the second heat exchange section is connected to the second port of the compressor (1) and the second heat exchanger (4) respectively through parallel pipelines.

6. The thermal management system as described in claim 1, characterized in that, A fourth main circuit (16) is also provided, which is connected to the inlet of the compressor (1) in the cooling mode and to the outlet of the compressor (1) in the heating mode; The second port of the second heat exchanger (4) is provided with a second main line (13); The first port of the first heat exchanger (5) is connected to the second main line (13) through the third branch (14) and to the fourth main line (16) through the sixth branch (15) which is in parallel with the third branch (14); the second port of the second heat exchange section is connected to the second main line (13) through the fourth branch (18) and to the fourth main line (16) through the fifth branch (19); One-way valves are provided on the third branch (14), the fourth branch (18), the fifth branch (19) and the sixth branch (15).

7. The thermal management system as described in claim 6, characterized in that, It also includes a multi-way valve (6), the compressor (1) is provided with a return main line (8) at the outlet and an outflow main line (7) at the inlet, the first valve port of the multi-way valve (6) is connected to the outflow main line (7), the second valve port is connected to the pipeline connecting the first port of the first heat exchange section, the third valve port is connected to the return main line (8), and the fourth valve port is connected to the fourth main line (16); In cooling mode, the fourth valve port is connected to the first valve port, and the third valve port is connected to the second valve port; in heating mode, the first valve port is connected to the second valve port, and the third valve port is connected to the fourth valve port.

8. An energy storage container, characterized in that, It includes the thermal management system as described in any one of claims 1-7.

9. A control method for a thermal management system, characterized in that, The thermal management system applicable to any one of claims 1-7 includes the following steps: Determine if it is in heating mode. If so, the pressure regulating valve (2) is opened so that the refrigerant flowing from the compressor (1) flows into the pressure regulating valve (2) and then flows into the second heat exchanger (4) after passing through the first heat exchange section of the pressure regulating valve (2) and the third heat exchanger (3) in sequence.

10. The control method for the thermal management system as described in claim 9, characterized in that, It also includes the following steps: The pressure and / or temperature values ​​at the two ports of the second heat exchanger (4) are detected. If the detection results exceed the preset range, the opening of the pressure regulating valve (2) is adjusted according to the detection results to reduce the temperature difference between the two ports of the second heat exchanger (4).

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