Thermal management system and method of controlling the same, energy storage container

Abstract

The application provides a heat management system and a control method thereof and an energy storage container, which are used for heat exchange of multiple batteries in an energy storage system and include a refrigerant main loop having a compressor, a first heat exchanger, a second heat exchanger and a third heat exchanger, the third heat exchanger has a first heat exchange part and a second heat exchange part, the inlet of the compressor is communicated with the second heat exchanger through the first heat exchange part, and the outlet of the compressor is communicated with the first heat exchanger through the second heat exchange part; a first refrigerant bypass is respectively communicated with the inlet and the outlet of the second heat exchanger; and a second refrigerant bypass is respectively communicated with the inlet and the outlet of the compressor. In this way, the refrigerant flowing out of the first heat exchanger and flowing to the inlet of the compressor is first heated by the third heat exchanger, and then mixed with high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor to replace the function of the second heat exchanger in evaporating and absorbing heat, so that the problem of poor heating efficiency of the compressor in an extremely low-temperature environment can be solved.

Description

Technical Field

[0001] This application relates to the field of energy storage system technology, specifically to a thermal management system and its control method, and an energy storage container. Background Technology

[0002] Energy storage technology can alter the real-time characteristics of power transmission, making electricity use more flexible. It is a strategic supporting technology for energy structure transformation and changes in electricity production and consumption patterns. With the increasing demand for energy storage, temperature control of energy storage systems is a crucial aspect of ensuring their normal operation.

[0003] In the process of realizing this invention, the inventors discovered at least the following technical problems in the prior art:

[0004] In existing technologies, temperature control of energy storage batteries generally adopts direct cooling, using a refrigerant as the heat transfer medium. Heat exchange with the energy storage battery is completed through the flow and phase change of the refrigerant. However, under extremely low ambient temperatures, the heating capacity of the thermal management unit for the energy storage battery drops sharply. Traditional heat pump heating cannot guarantee sufficient heating capacity or may even completely lose its heating capacity, thus failing to effectively heat the battery cells and causing the energy storage system to malfunction. Summary of the Invention

[0005] In view of this, this application provides a thermal management system and its control method, and an energy storage container, which can at least improve the heating efficiency of the compressor in the thermal management system in extremely low temperature environments.

[0006] To achieve the above objectives, this application provides the following technical solution:

[0007] A thermal management system for heat exchange of multiple batteries in an energy storage system, comprising:

[0008] The refrigerant main circuit includes a compressor, a first heat exchanger, a second heat exchanger, and a third heat exchanger. 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. The inlet of the compressor is connected to the second heat exchanger through the first heat exchange section, and the outlet of the compressor is connected to the first heat exchanger through the second heat exchange section, so that the refrigerant flowing out of the second heat exchanger exchanges heat with the refrigerant flowing out of the compressor.

[0009] The first refrigerant bypass is connected to the inlet and outlet of the second heat exchanger respectively, so that the refrigerant flowing out of the first heat exchanger flows to the first heat exchange section;

[0010] The second refrigerant bypass is connected to the inlet and outlet of the compressor respectively, so that the refrigerant flowing out of the compressor mixes with the refrigerant flowing out of the first heat exchange section.

[0011] Optionally, both the first heat exchange section and the second refrigerant bypass are connected to the inlet of the compressor via the gas-liquid separator.

[0012] Optionally, the compressor is equipped with a first temperature sensor and a second temperature sensor at its inlet and outlet, respectively.

[0013] Optionally, a liquid receiver and a dryer are sequentially arranged between the outlet of the first heat exchanger and the inlet of the second heat exchanger.

[0014] Optionally, multiple first heat exchangers are provided and connected in parallel between the second heat exchange section and the second heat exchanger.

[0015] Optionally, the first refrigerant bypass has a first valve to regulate the refrigerant flow rate of the first refrigerant bypass.

[0016] Optionally, the second refrigerant bypass has a second valve to regulate the refrigerant flow rate of the second refrigerant bypass.

[0017] Optionally, a third valve is provided between the compressor outlet and the second heat exchange section to regulate the refrigerant flow to the second heat exchange section.

[0018] Optionally, a multi-port valve is included, wherein the first and second ports of the multi-port valve are respectively connected to the outlet of the compressor and the first heat exchange section, and the third and fourth ports of the multi-port valve are respectively connected to the inlet of the compressor and the second heat exchange section. In different modes, the first port, the second port, the third port and the fourth port are connected in pairs.

[0019] An energy storage container includes a thermal management system as described in any of the preceding claims.

[0020] The thermal management system and control method, and energy storage container provided in this application, in heating mode, compress low-pressure gaseous refrigerant into high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant flowing out of the compressor outlet first flows through the second heat exchange section, and then through the first heat exchanger. Meanwhile, the room-temperature liquid refrigerant condensed in the first heat exchanger first flows through the second heat exchanger for evaporation and heat absorption, then flows through the first heat exchange section, and finally flows back to the compressor inlet. Since the refrigerant temperature in the first heat exchange section is lower than that in the second heat exchange section, the refrigerant flowing out of the second heat exchanger can exchange heat with the refrigerant flowing out of the compressor through the third heat exchanger. This can eliminate the overheating section of the refrigerant flowing to the first heat exchanger, improve the temperature uniformity in the first heat exchanger, and increase the temperature of the refrigerant flowing back to the compressor inlet, thereby increasing the proportion of gaseous refrigerant flowing back to the compressor. In extremely low temperature environments, the second heat exchanger absorbs very little heat or does not work (it cannot perform evaporative heat absorption). The room-temperature liquid refrigerant flowing out of the first heat exchanger skips the second heat exchanger and flows through the first heat exchange section to exchange heat and raise its temperature (at this time, the third heat exchanger replaces the second heat exchanger and plays the role of evaporative heat absorption). Then it mixes and heats up with the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor outlet, thus replacing the evaporative heat absorption function of the second heat exchanger. By making all the heat sources in the refrigerant main circuit come from the power of the compressor itself, the problem of poor compressor thermal efficiency in extremely low temperature environments can be solved, thereby improving the stability and service life of the battery. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of this application. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0022] Figure 1 This is a schematic diagram illustrating a heating mode in an extremely low temperature environment, as shown in some embodiments.

[0023] In the diagram: 1. Compressor; 2. Second temperature sensor; 3. Multi-way valve; 4. Third valve; 5. Second valve; 6. Third heat exchanger; 7. First heat exchanger; 8. Liquid receiver; 9. Dryer; 10. Second heat exchanger; 11. First valve; 12. Gas-liquid separator; 13. First temperature sensor. Detailed Implementation

[0024] 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.

[0025] like Figure 1 As shown, this application embodiment provides a thermal management system for heat exchange of multiple batteries (which can be used for photovoltaic energy storage or wind power energy storage) in an energy storage system, so as to keep the battery temperature within a reasonable range. This system is mainly used for heating batteries in extremely low temperature environments. The thermal management system includes a refrigerant main circuit, a first refrigerant bypass, and a second refrigerant bypass. The first and second refrigerant bypasses are connected in parallel with a portion of a branch in the refrigerant main circuit to form new refrigerant flow paths.

[0026] The refrigerant main circuit includes a compressor 1, a first heat exchanger 7, a second heat exchanger 10, and a third heat exchanger 6. The first heat exchanger 7 directly heats the battery; for example, it can be configured as a heat exchange plate, where the refrigerant flows and undergoes phase change, carrying away heat from the battery. The second heat exchanger 10 is located in the external environment outside the battery and functions as an evaporative heat absorber. The third heat exchanger 6 has a first heat exchange section and a second heat exchange section, which can exchange heat. For example, the first and second heat exchange sections can be configured as two adjacent heat exchange pipes within the third heat exchanger 6. A throttling component connects the first heat exchanger 7 and the second heat exchanger 10 to regulate the refrigerant flow rate and pressure. The inlet of the compressor 1 connects to the second heat exchanger 10 through the first heat exchange section, and the outlet of the compressor 1 connects to the first heat exchanger 7 through the second heat exchange section, thus connecting the compressor 1, the third heat exchanger 6, the first heat exchanger 7, and the second heat exchanger 10 to form a refrigerant flow circuit.

[0027] In heating mode, compressor 1 compresses low-pressure gaseous refrigerant into high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant flowing out of compressor 1 first flows through the second heat exchange section, and then through the first heat exchanger 7. Meanwhile, the room-temperature liquid refrigerant condensed in the first heat exchanger 7 first flows through the second heat exchanger 10 to evaporate and absorb heat, then flows through the first heat exchange section, and finally flows back to the inlet of compressor 1. Since the temperature of the refrigerant in the first heat exchange section is lower than that in the second heat exchange section, the refrigerant flowing out of the second heat exchanger 10 can exchange heat with the refrigerant flowing out of compressor 1 through the third heat exchanger 6. This can eliminate the overheating section of the refrigerant flowing to the first heat exchanger 7, improve the temperature uniformity in the first heat exchanger 7, and increase the temperature of the refrigerant flowing back to the inlet of compressor 1, thereby increasing the proportion of gaseous refrigerant flowing back to compressor 1.

[0028] The first refrigerant bypass connects to the inlet and outlet of the second heat exchanger 10, respectively. This design reduces the refrigerant flow rate within the second heat exchanger 10, allowing the refrigerant exiting the first heat exchanger 7 to flow directly to the first heat exchange section. Furthermore, the second refrigerant bypass connects to the inlet and outlet of the compressor 1, respectively. This design splits the high-temperature, high-pressure gaseous refrigerant exiting the compressor 1 into two paths: one flows to the second heat exchange section and the first heat exchanger 7, while the other mixes with the refrigerant exiting the first heat exchange section and flows directly to the inlet of the compressor 1.

[0029] In extremely low temperature environments, the second heat exchanger 10 absorbs very little heat or does not work (it cannot perform evaporation and heat absorption). The room-temperature liquid refrigerant flowing out of the first heat exchanger 7 skips the second heat exchanger 10 and first flows through the first heat exchange section to exchange heat and raise its temperature (at this time, the third heat exchanger 6 replaces the second heat exchanger 10 and plays the role of evaporation and heat absorption). Then it mixes with the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 1 outlet to raise its temperature and form a low-pressure gaseous refrigerant.

[0030] Thus, when heating in extremely low temperature environments, the refrigerant flowing out of the first heat exchanger 7 and into the compressor 1 inlet first undergoes heat exchange and temperature rise through the third heat exchanger 6, and then mixes and heats up with the high-temperature, high-pressure gaseous refrigerant flowing out of the compressor 1 outlet, replacing the evaporation and heat absorption function of the second heat exchanger 10. By making all the heat sources in the refrigerant main circuit come from the power of the compressor 1 itself, the problem of poor compressor thermal efficiency in extremely low temperature environments can be solved, thereby improving the stability and lifespan of the battery.

[0031] It is understandable that when this system is only used in extremely low temperature environments, the second heat exchanger 10 can be omitted, and only the first refrigerant bypass can be retained, so that the liquid refrigerant flowing out of the first heat exchanger 7 can flow directly through the first refrigerant bypass to the first heat exchange section of the third heat exchanger 6, and then mix with the high temperature and high pressure gaseous refrigerant flowing out of the compressor 1 outlet.

[0032] In some embodiments, a gas-liquid separator 12 is provided at the inlet of compressor 1, and both the first heat exchange section and the second refrigerant bypass are connected to the inlet of compressor 1 through the gas-liquid separator 12. Since the refrigerant flowing out of compressor 1 and the refrigerant flowing out of the first heat exchange section are in a two-phase state of gas and liquid after mixing, the liquid refrigerant can be separated by the gas-liquid separator 12, ensuring that the refrigerant flowing into the inlet of compressor 1 is in a gaseous state, thereby improving the safety and stability of the system.

[0033] The compressor 1 is equipped with a first temperature sensor 13 at its inlet and a second temperature sensor 2 at its outlet. The temperature difference between the inlet and outlet of the compressor 1 can be detected by the first temperature sensor 13 and the second temperature sensor 2, and the working status of the compressor 1 and the thermal management system can be adjusted according to the temperature difference.

[0034] A liquid receiver 8 and a dryer 9 are sequentially arranged between the outlet of the first heat exchanger 7 and the inlet of the second heat exchanger 10. The liquid receiver 8 serves to store refrigerant, separate gas-liquid refrigerant, and buffer pressure in the main refrigerant circuit. The dryer 9 absorbs moisture from the refrigerant and filters impurities in the refrigerant. In heating mode, the room-temperature liquid refrigerant flowing out of the first heat exchanger 7 first flows through the liquid receiver 8 and then through the dryer 9, which improves the stability and reliability of the refrigerant entering the second heat exchanger 10.

[0035] Multiple first heat exchangers 7 are connected in parallel, and each first heat exchanger 7 is connected between the second heat exchange section and the second heat exchanger 10. Thus, multiple first heat exchangers 7 can be used to exchange heat with multiple batteries. The number of first heat exchangers 7 can be the same as the number of batteries; for example, four sets of first heat exchangers 7 and batteries can be configured one-to-one. Alternatively, the number of first heat exchangers 7 and batteries can be different; for example, multiple first heat exchangers 7 can simultaneously heat the same battery, or a single first heat exchanger 7 can simultaneously heat multiple batteries. Specifically, branch heads and / or manifolds can be used upstream or downstream of the multiple first heat exchangers 7 to achieve flow distribution between one or multiple paths, thereby ensuring uniform heat exchange performance of each first heat exchanger 7.

[0036] In some embodiments, the first refrigerant bypass has a first valve 11. By controlling the first valve 11, the flow rate of the first refrigerant bypass can be adjusted. During use, the flow rate of the first refrigerant bypass can be adjusted according to the actual temperature of the external environment, keeping the ratio of refrigerant flowing through the second heat exchanger 10 to refrigerant flowing through the first refrigerant bypass within a reasonable range. This facilitates adaptive control based on actual conditions and has a wide range of applications. Specifically, the first valve 11 is configured as a solenoid valve, which is beneficial for realizing automatic control of the system.

[0037] The second refrigerant bypass has a second valve 5, which regulates the flow rate of the second refrigerant bypass. During operation, the flow rate of the second refrigerant bypass can be adjusted according to the actual temperature of the external environment, thereby adjusting the refrigerant distribution ratio from the compressor 1 outlet to a reasonable range. This means controlling the ratio of refrigerant flowing back to the compressor 1 inlet to the refrigerant flowing to the second heat exchanger within a reasonable range, facilitating adaptive control based on actual conditions and broadening its application range. Furthermore, the second valve 5 has an isenthalpic pressure-reducing hot gas bypass function. Through hot gas bypass, the compressor mass flow rate is increased, the pressure ratio is increased, and the compressor power is increased to enhance heating capacity. Secondly, the hot gas bypass mixes with the low-pressure refrigerant in the third heat exchanger of the main circuit, increasing the superheat at the compressor suction port. Since all heating in this mode originates from the compressor's power, bypassing is necessary to increase the compressor mass flow rate and power, thereby increasing heating capacity. Specifically, the second valve 5 is configured as an electronic expansion valve, which facilitates automatic system control.

[0038] Furthermore, a third valve 4 is installed between the outlet of compressor 1 and the second heat exchange section. By controlling the third valve 4, the flow rate of refrigerant flowing to the second heat exchange section can be adjusted. This not only allows for the adjustment of the refrigerant distribution ratio from the outlet of compressor 1 through the cooperation of the second valve 5 and the third valve 4, but also allows the third valve 4 to reduce pressure, thereby eliminating superheat of the refrigerant flowing into the first heat exchanger 7 and improving the temperature uniformity within the first heat exchanger 7. Moreover, the third valve 4 also has an isenthalpic pressure reduction function, increasing the compressor power by increasing the pressure ratio to increase the heating capacity. Since all heating in this mode comes from the compressor's power, a pressure reducing valve is needed to increase the compressor's discharge pressure, thereby increasing the heating capacity.

[0039] This thermal management system also includes a multi-way valve 3. For example, the multi-way valve 3 is configured as a four-channel valve with a first interface, a second interface, a third interface, and a fourth interface. The first and second interfaces of the multi-way valve 3 are respectively connected to the outlet of the compressor 1 and the first heat exchange section. The third and fourth interfaces of the multi-way valve 3 are respectively connected to the inlet of the compressor 1 and the second heat exchange section. In different modes, the first, second, third, and fourth interfaces are connected in pairs. Specifically, in the heating mode, the multi-way valve 3 is in the first state, with the first and second interfaces connected, and the third and fourth interfaces connected. The high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 first flows through the second heat exchange section of the third heat exchanger 6, and then flows through the first heat exchanger 7, so as to heat the battery by condensing and dissipating heat in the first heat exchanger 7.

[0040] It should be noted that the inlet and outlet of compressor 1, the inlet and outlet of the first heat exchanger 7, and the inlet and outlet of the second heat exchanger 10 in this article all describe the system in heating mode. That is, in heating mode, the refrigerant flows from the inlet to the outlet. Conversely, in cooling mode, the operating states of the first heat exchanger 7 and the second heat exchanger 10 are reversed so that the refrigerant flows from the outlet to the inlet. In particular, due to the multi-way valve 3, in both cooling and heating modes, the refrigerant flows from the inlet to the outlet of compressor 1.

[0041] In cooling mode, multi-way valve 3 is in its second state, with the first and fourth ports connected, and the second and third ports connected. The high-temperature, high-pressure gaseous refrigerant flowing from the compressor 1 outlet first flows through the first heat exchange section of the third heat exchanger 6, then through the second heat exchanger 10, where it condenses and dissipates heat to form a room-temperature liquid refrigerant. The liquid refrigerant then flows through the first heat exchanger 7, then through the second heat exchange section of the third heat exchanger 6, and finally returns to the compressor 1 inlet. There, the liquid refrigerant evaporates and absorbs heat in the first heat exchanger 7, cooling the battery.

[0042] This application provides a control method for a thermal management system, based on the thermal management system described in the above embodiments, including:

[0043] In heating mode, determine whether the ambient temperature is lower than the preset value;

[0044] If so, the first valve is opened to allow the refrigerant from the first heat exchanger to flow to the compressor inlet through the first refrigerant bypass and the first heat exchange section, and the second valve is opened to allow the refrigerant from the compressor to be diverted to the compressor inlet through the second refrigerant bypass.

[0045] In extremely low temperature environments, the second heat exchanger 10 absorbs very little heat or does not work (it cannot perform evaporation and heat absorption). The room-temperature liquid refrigerant flowing out of the first heat exchanger 7 skips the second heat exchanger 10 and first flows through the first heat exchange section to exchange heat and raise its temperature (at this time, the third heat exchanger 6 replaces the second heat exchanger 10 and plays the role of evaporation and heat absorption). Then it mixes with the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor 1 outlet to raise its temperature and form a low-pressure gaseous refrigerant.

[0046] Thus, when heating in extremely low temperature environments, the refrigerant flowing out of the first heat exchanger 7 and into the compressor 1 first undergoes heat exchange and temperature rise through the third heat exchanger 6, and then mixes and heats up with the high-temperature, high-pressure gaseous refrigerant flowing out of the compressor 1, replacing the evaporation and heat absorption function of the second heat exchanger 10. By making all the heat sources in the refrigerant main circuit come from the power of the compressor 1 itself, the problem of poor compressor thermal efficiency in extremely low temperature environments can be solved, thereby improving the stability and service life of the energy storage battery.

[0047] This application provides an energy storage container, including the thermal management system described in the above embodiment. With this configuration, when heating in extremely low temperature environments, the refrigerant flowing from the first heat exchanger 7 to the inlet of the compressor 1 first undergoes heat exchange and temperature rise through the third heat exchanger 6, and then mixes and heats up with the high-temperature, high-pressure gaseous refrigerant flowing from the outlet of the compressor 1, replacing the evaporative heat absorption function of the second heat exchanger 10. By ensuring that all heat sources in the refrigerant main circuit come from the power of the compressor 1 itself, the problem of slow heat exchange efficiency in extremely low temperature environments can be solved.

[0048] 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.

[0049] The block diagrams of devices, apparatuses, devices, and systems involved 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 block diagrams. As those skilled in the art will recognize, these devices, apparatuses, devices, and systems 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 terms “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.

[0050] It should also be noted that in the apparatus, equipment, and methods of this application, the components or steps can be disassembled and / or recombined. These disassemblies and / or recombinations should be considered as equivalent solutions of this application.

[0051] 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.

[0052] It should be understood that the qualifiers “first,” “second,” “third,” “fourth,” “fifth,” and “sixth” used in the description of the embodiments of this application are only used to more clearly illustrate the technical solutions and are not intended to limit the scope of protection of this application.

[0053] 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.

Claims

1. A thermal management system, characterized in that, Used for heat exchange of multiple batteries in an energy storage system, including: The refrigerant main circuit includes a compressor, a first heat exchanger, a second heat exchanger, and a third heat exchanger. 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. The inlet of the compressor is connected to the second heat exchanger through the first heat exchange section, and the outlet of the compressor is connected to the first heat exchanger through the second heat exchange section, so that the refrigerant flowing out of the second heat exchanger exchanges heat with the refrigerant flowing out of the compressor. A first refrigerant bypass is connected to the inlet and outlet of the second heat exchanger, so that the refrigerant flowing out of the first heat exchanger flows to the first heat exchange section; and the first refrigerant bypass has a first valve for adjusting the refrigerant flow rate of the first refrigerant bypass. The second refrigerant bypass is connected to the inlet and outlet of the compressor respectively, so as to mix the refrigerant flowing out of the compressor with the refrigerant flowing out of the first heat exchange section; and the second refrigerant bypass has a second valve to adjust the refrigerant flow rate of the second refrigerant bypass. In heating mode, the refrigerant flowing out of the compressor outlet flows sequentially through the second heat exchange section, the first heat exchanger, the second heat exchanger, the first heat exchange section, and the compressor inlet. When the second heat exchanger is not working, the refrigerant flowing out of the first heat exchanger skips the second heat exchanger, flows through the first heat exchange section for heat exchange, and then mixes with the refrigerant flowing out of the compressor outlet.

2. The thermal management system according to claim 1, characterized in that, Both the first heat exchange section and the second refrigerant bypass are connected to the inlet of the compressor via a gas-liquid separator.

3. The thermal management system according to claim 1, characterized in that, The compressor is equipped with a first temperature sensor and a second temperature sensor at its inlet and outlet, respectively.

4. The thermal management system according to claim 1, characterized in that, A liquid receiver and a dryer are sequentially installed between the outlet of the first heat exchanger and the inlet of the second heat exchanger.

5. The thermal management system according to claim 1, characterized in that, Multiple first heat exchangers are provided and connected in parallel between the second heat exchange section and the second heat exchanger.

6. The thermal management system according to claim 5, characterized in that, A third valve is provided between the compressor outlet and the second heat exchange section to regulate the refrigerant flow rate to the second heat exchange section.

7. The thermal management system according to claim 1, characterized in that, The system includes a multi-port valve, wherein the first and second ports of the multi-port valve are respectively connected to the outlet of the compressor and the first heat exchange section, and the third and fourth ports of the multi-port valve are respectively connected to the inlet of the compressor and the second heat exchange section. In different modes, different ports among the first, second, third and fourth ports are connected in pairs.

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, based on the thermal management system according to any one of claims 1-7, comprising: In heating mode, determine whether the ambient temperature is lower than the preset value; If so, the first valve is opened to allow the refrigerant from the first heat exchanger to flow to the compressor inlet through the first refrigerant bypass and the first heat exchange section, and the second valve is opened to allow the refrigerant from the compressor to be diverted to the compressor inlet through the second refrigerant bypass.

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