Thermal management system, control method thereof and energy storage container

Abstract

The invention provides a heat management system, a control method thereof and an energy storage container, the heat management system is used for carrying out heat exchange on a plurality of batteries in an energy storage system, and the heat management system comprises a refrigerant main loop which is provided with a compressor, a first heat exchanger, a second heat exchanger and a third heat exchanger, and the third heat exchanger is provided with a first heat exchange part and a second heat exchange part; an inlet of the compressor communicates with the second heat exchanger through the first heat exchange part. An outlet of the compressor communicates with the first heat exchanger through the second heat exchange part. The first refrigerant bypass communicates with an inlet and an outlet of the second heat exchanger. The second refrigerant bypass communicates with an inlet and an outlet of the compressor. Thus, the refrigerant flowing out of the first heat exchanger and flowing to the inlet of the compressor is firstly subjected to heat exchange and temperature rise through the third heat exchanger and then mixed with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor for temperature rise, the effect of evaporation heat absorption of the second heat exchanger is replaced, and the problem that the compressor is poor in heating efficiency in the extremely low-temperature environment can be solved.

Description

Technical Field

[0001] The present application relates to the technical field of energy storage systems, and in particular to a thermal management system and a control method thereof, and an energy storage container. Background Art

[0002] Energy storage technology can change the real-time characteristics of power transmission and make the use of electricity more flexible. It is a strategic support technology for the transformation of energy structure and the transformation of power production and consumption. With the continuous increase in energy storage demand, temperature control of energy storage system is a key link to ensure the normal operation of the system.

[0003] In the process of implementing the present invention, the inventors found that there are at least the following technical problems in the prior art:

[0004] In the prior art, the temperature control of energy storage batteries generally adopts direct cooling, using refrigerant as the heat transfer medium, and completing the heat exchange of the energy storage battery 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, and the traditional heat pump heating cannot guarantee sufficient heating capacity or even completely loses the heating capacity, and thus cannot effectively heat the battery cell, causing the energy storage system to fail to work. Summary of the invention

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

[0006] In order to achieve the above objectives, this application provides the following technical solutions:

[0007] A thermal management system for exchanging heat for a plurality of batteries in an energy storage system, comprising:

[0008] A refrigerant main circuit comprises a compressor, a first heat exchanger, a second heat exchanger and a third heat exchanger, wherein the third heat exchanger comprises a first heat exchange portion and a second heat exchange portion for exchanging heat with the first heat exchange portion, the inlet of the compressor is connected to the second heat exchanger through the first heat exchange portion, and the outlet of the compressor is connected to the first heat exchanger through the second heat exchange portion, so that the refrigerant flowing out of the second heat exchanger exchanges heat with the refrigerant flowing out of the compressor;

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

[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 is mixed with the refrigerant flowing out of the first heat exchange part.

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

[0012] Optionally, the inlet and outlet of the compressor are respectively provided with a first temperature sensor and a second temperature sensor.

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

[0014] Optionally, a plurality of the first heat exchangers are provided and are connected in parallel between the second heat exchange part and the second heat exchanger.

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

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

[0017] Optionally, a third valve is provided between the outlet of the compressor and the second heat exchange part to adjust the flow rate of the refrigerant flowing to the second heat exchange part.

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

[0019] An energy storage container comprises a thermal management system as described in any one of the above items.

[0020] The thermal management system and its control method, as well as the energy storage container provided by the present application, are such that in the heating mode, the compressor compresses the low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant flowing out of the compressor outlet first flows through the second heat exchange part, and then flows through the first heat exchanger. The liquid refrigerant at room temperature condensed by the first heat exchanger first flows through the second heat exchanger for evaporation and heat absorption, then flows through the first heat exchange part, and finally flows back to the inlet of the compressor. Since the temperature of the refrigerant in the first heat exchange part is lower than the temperature of the refrigerant in the second heat exchange part, the refrigerant flowing out of the second heat exchanger can be heat exchanged with the refrigerant flowing out of the compressor through the third heat exchanger, which can not only eliminate the overheating section of the refrigerant flowing to the first heat exchanger and improve the temperature uniformity in the first heat exchanger, but also increase the temperature of the refrigerant flowing back to the inlet of the compressor and increase the proportion of the gaseous refrigerant flowing back to the compressor. In an extremely low temperature environment, the second heat exchanger absorbs very little heat or does not work (cannot evaporate and absorb heat). The liquid refrigerant at room temperature flowing out of the first heat exchanger skips the second heat exchanger and first flows through the first heat exchange part for heat exchange and temperature rise (at this time, the third heat exchanger replaces the second heat exchanger and plays a role of evaporation and heat absorption). It is then mixed and heated with the high-temperature and high-pressure gaseous refrigerant flowing out of the compressor outlet to replace the role of evaporation and heat absorption of the second heat exchanger. By making all the heat sources in the refrigerant main circuit come from the power of the compressor's own operation, the problem of poor thermal efficiency of the compressor in an extremely low temperature environment can be solved, thereby improving the stability and service life of the battery. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0022] Figure 1 It is a schematic diagram of a heating mode in an extremely low temperature environment according to some embodiments.

[0023] In the figure: 1. compressor; 2. second temperature sensor; 3. multi-way valve; 4. third valve member; 5. second valve member; 6. third heat exchanger; 7. first heat exchanger; 8. liquid storage device; 9. dryer; 10. second heat exchanger; 11. first valve member; 12. gas-liquid separator; 13. first temperature sensor. DETAILED DESCRIPTION

[0024] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0025] like Figure 1 As shown, an embodiment of the present application provides a thermal management system for exchanging heat for multiple batteries in an energy storage system (the batteries can be used for photovoltaic energy storage or wind energy storage) to keep the temperature of the batteries within a reasonable range, and is mainly used to heat the batteries in an extremely low temperature environment. The thermal management system includes a refrigerant main circuit, a first refrigerant bypass, and a second refrigerant bypass. The first refrigerant bypass and the second refrigerant bypass are respectively connected in parallel with a part of the branches in the refrigerant main circuit to form a new refrigerant flow path.

[0026] The refrigerant main circuit has a compressor 1, a first heat exchanger 7, a second heat exchanger 10 and a third heat exchanger 6, wherein the first heat exchanger 7 is used to directly exchange heat with the battery, for example, the first heat exchanger 7 is set as a heat exchange plate, and the heat in the battery is taken away by the flow and phase change of the refrigerant in the heat exchange plate. The second heat exchanger 10 is in the external environment outside the battery, and plays the role of evaporation and heat absorption. The third heat exchanger 6 has a first heat exchange part and a second heat exchange part, and the third heat exchanger 6 can exchange heat through the first heat exchange part and the second heat exchange part, for example, the first heat exchange part and the second heat exchange part are set as two adjacent heat exchange pipelines in the third heat exchanger 6. A throttling component is connected between the first heat exchanger 7 and the second heat exchanger 10 to adjust the flow and pressure of the refrigerant. The inlet of the compressor 1 is connected to the second heat exchanger 10 through the first heat exchange part, and the outlet of the compressor 1 is connected to the first heat exchanger 7 through the second heat exchange part, so that the compressor 1, the third heat exchanger 6, the first heat exchanger 7 and the second heat exchanger 10 are connected to form a loop for the flow of refrigerant.

[0027] In the heating mode, the compressor 1 compresses the low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 first flows through the second heat exchange part, and then flows through the first heat exchanger 7. The liquid refrigerant at room temperature condensed by the first heat exchanger 7 first flows through the second heat exchanger 10 for evaporation and heat absorption, then flows through the first heat exchange part, and finally flows back to the inlet of the compressor 1. Since the refrigerant temperature in the first heat exchange part is lower than the refrigerant temperature in the second heat exchange part, the refrigerant flowing out of the second heat exchanger 10 can be heat exchanged with the refrigerant flowing out of the compressor 1 through the third heat exchanger 6, which can not only eliminate the overheating section of the refrigerant flowing to the first heat exchanger 7 and improve the temperature uniformity in the first heat exchanger 7, but also increase the temperature of the refrigerant flowing back to the inlet of the compressor 1 and increase the proportion of the gaseous refrigerant flowing back to the compressor 1.

[0028] The two ends of the first refrigerant bypass are respectively connected to the inlet and outlet of the second heat exchanger 10. The design of the first refrigerant bypass can reduce the refrigerant flow in the second heat exchanger 10, so that the refrigerant flowing out of the first heat exchanger 7 flows directly to the first heat exchange part. In addition, the two ends of the second refrigerant bypass are respectively connected to the inlet and outlet of the compressor 1. The design of the second refrigerant bypass can divide the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 into two paths, one of which flows to the second heat exchange part and the first heat exchanger 7, and the other flows directly to the inlet of the compressor 1 after mixing with the refrigerant flowing out of the first heat exchange part.

[0029] In an extremely low temperature environment, the second heat exchanger 10 absorbs very little heat or does not work (cannot evaporate and absorb heat). The liquid refrigerant at room temperature flowing out of the first heat exchanger 7 skips the second heat exchanger 10, first flows through the first heat exchange part for heat exchange and temperature rise (at this time, the third heat exchanger 6 replaces the second heat exchanger 10 and plays a role of evaporation and heat absorption), and then mixes with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 to be heated and mixed to form a low-pressure gaseous refrigerant.

[0030] In this way, when heating in an extremely low temperature environment, the refrigerant flowing out of the first heat exchanger 7 and flowing to the inlet of the compressor 1 is first heated by heat exchange through the third heat exchanger 6, and then mixed and heated with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1, so as to replace the evaporation and heat absorption effect 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's own operation, the problem of poor thermal efficiency of the compressor in an extremely low temperature environment can be solved, thereby improving the stability and service life of the battery.

[0031] It can be understood that when the system is only used in an extremely low temperature environment, 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 flows directly through the first refrigerant bypass to the first heat exchange part of the third heat exchanger 6, and then mixes with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1.

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

[0033] A first temperature sensor 13 is provided at the inlet of the compressor 1, and a second temperature sensor 2 is provided at the outlet of the compressor 1. The first temperature sensor 13 and the second temperature sensor 2 can detect the temperature difference between the inlet and outlet of the compressor 1, and then the working state of the compressor 1 and the working state of the thermal management system can be regulated according to the temperature difference.

[0034] A liquid reservoir 8 and a dryer 9 are arranged in sequence between the outlet of the first heat exchanger 7 and the inlet of the second heat exchanger 10, wherein the liquid reservoir 8 can store refrigerant, separate gas-liquid refrigerant, and buffer pressure in the refrigerant main circuit, and the dryer 9 can absorb moisture in the refrigerant and filter impurities in the refrigerant in the refrigerant main circuit. In the heating mode, the liquid refrigerant at room temperature flowing out of the first heat exchanger 7 first flows through the liquid reservoir 8 and then flows through the dryer 9, which can improve the stability and reliability of the refrigerant entering the second heat exchanger 10.

[0035] There are multiple first heat exchangers 7 arranged in parallel, and each first heat exchanger 7 is connected between the second heat exchange part and the second heat exchanger 10. In this way, heat exchange of multiple batteries can be achieved through multiple first heat exchangers 7. Among them, the number of first heat exchangers 7 and the number of batteries can be consistent, for example, four groups of first heat exchangers 7 and batteries are arranged one-to-one. In addition, the number of first heat exchangers 7 and batteries can be inconsistent, for example, multiple first heat exchangers 7 perform heat exchange on the same battery at the same time, or the same first heat exchanger 7 performs heat exchange on multiple batteries at the same time. Specifically, a connection form of a branch head and / or a branch pipe can be used upstream or downstream of multiple first heat exchangers 7 to achieve diversion between one path and multiple paths, thereby ensuring uniform heat exchange effect of each first heat exchanger 7.

[0036] In some embodiments, the first refrigerant bypass has a first valve member 11, and the flow of the first refrigerant bypass can be adjusted by controlling the first valve member 11. When in use, the flow of the first refrigerant bypass can be adjusted according to the actual temperature in the external environment, and the ratio of the refrigerant flowing through the second heat exchanger 10 and the refrigerant flowing through the first refrigerant bypass can be controlled within a reasonable range, which is conducive to adaptive control according to actual conditions and has a wide range of applications. Specifically, the first valve member 11 is set as a solenoid valve, which is conducive to realizing automatic control of the system.

[0037] The second refrigerant bypass has a second valve 5, and the flow of the second refrigerant bypass can be adjusted by controlling the second valve 5. When in use, the flow of the second refrigerant bypass can be adjusted according to the actual temperature in the external environment, and then the diversion ratio of the refrigerant flowing out of the outlet of the compressor 1 is adjusted to a reasonable range, that is, the ratio of the refrigerant flowing back to the inlet of the compressor 1 and the refrigerant flowing to the second heat exchange part is controlled within a reasonable range, which is conducive to adaptive control according to actual conditions and has a wide range of applications. Moreover, the second valve 5 has the function of isenthalpic decompression hot gas bypass. Through the hot gas bypass, the compressor mass flow rate is increased, the pressure ratio is increased, and the compressor power is increased to increase the heating capacity. Secondly, the hot gas bypass is mixed with the low-pressure refrigerant of the third heat exchanger of the main circuit to increase the superheat of the compressor suction port. Since in this mode, all the heating comes from the power of the compressor, it is necessary to use a bypass to increase the compressor mass flow rate to increase the power, thereby increasing the heating capacity. Specifically, the second valve 5 is set as an electronic expansion valve, which is conducive to realizing automatic control of the system.

[0038] Furthermore, a third valve member 4 is provided between the outlet of the compressor 1 and the second heat exchange part. The refrigerant flow to the second heat exchange part can be adjusted by controlling the third valve member 4. In this way, not only can the diversion ratio of the refrigerant flowing out of the outlet of the compressor 1 be adjusted by the cooperation of the second valve member 5 and the third valve member 4, but also the third valve member 4 can play a role of reducing pressure, thereby eliminating the superheat of the refrigerant flowing into the first heat exchanger 7 and improving the temperature uniformity in the first heat exchanger 7. Moreover, the third valve member 4 also has the function of isenthalpic decompression, which increases the compressor power by increasing the pressure ratio to increase the heating amount. Since in this mode, all the heating comes from the power of the compressor, it is necessary to use a pressure reducing valve to increase the compressor exhaust pressure to increase the heating amount.

[0039] The thermal management system also includes a multi-way valve 3. For example, the multi-way valve 3 is set to have four channels, with a first interface, a second interface, a third interface and a fourth interface. The first interface and the second interface of the multi-way valve 3 are connected to the outlet of the compressor 1 and the first heat exchange part respectively, and the third interface and the fourth interface of the multi-way valve 3 are connected to the inlet of the compressor 1 and the second heat exchange part respectively. In different modes, the first interface, the second interface, the third interface and the fourth interface are connected in pairs. Specifically, in the heating mode, the multi-way valve 3 is in the first state, the first interface and the second interface are connected, and the third interface and the fourth interface are 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 part 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 the 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 are all descriptions of the system in the heating state, that is, in the heating state, the refrigerant flows from the inlet to the outlet. Conversely, in the cooling state, the working states of the first heat exchanger 7 and the second heat exchanger 10 are interchanged so that the refrigerant flows from the outlet to the inlet. In particular, due to the setting of the multi-way valve 3, the refrigerant flows from the inlet of the compressor 1 to the outlet of the compressor 1 in both the cooling and heating states.

[0041] In the cooling mode, the multi-way valve 3 is in the second state, the first interface is connected to the fourth interface, and the second interface is connected to the third interface. The high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 first flows through the first heat exchange part of the third heat exchanger 6, and then flows through the second heat exchanger 10, so as to condense and dissipate heat in the second heat exchanger 10 to form a liquid refrigerant at room temperature. Then the liquid refrigerant first flows through the first heat exchanger 7, then flows through the second heat exchange part of the third heat exchanger 6, and finally flows back to the inlet of the compressor 1. The liquid refrigerant evaporates and absorbs heat in the first heat exchanger 7 to cool the battery.

[0042] The present application embodiment provides a control method for a thermal management system, based on the thermal management system in the above embodiment, including:

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

[0044] If so, the first valve is controlled to open so that the refrigerant of the first heat exchanger flows to the inlet of the compressor through the second refrigerant bypass and the first heat exchange part, and the second valve is controlled to open so that the refrigerant of the compressor is diverted to the inlet of the compressor through the first refrigerant bypass.

[0045] Among them, in an extremely low temperature environment, the second heat exchanger 10 absorbs very little heat or does not work (cannot evaporate and absorb heat), and the liquid refrigerant at room temperature flowing out of the first heat exchanger 7 skips the second heat exchanger 10, first flows through the first heat exchange part for heat exchange and temperature rise (at this time, the third heat exchanger 6 replaces the second heat exchanger 10 and plays the role of evaporation and heat absorption), and then mixes and heats up with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 to form a low-pressure gaseous refrigerant.

[0046] In this way, when heating in an extremely low temperature environment, the refrigerant flowing out of the first heat exchanger 7 and flowing to the inlet of the compressor 1 is first heated by heat exchange through the third heat exchanger 6, and then mixed with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1 to be heated, so as to replace the evaporation and heat absorption effect 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's own operation, the problem of poor thermal efficiency of the compressor in an extremely low temperature environment can be solved, thereby improving the stability and service life of the energy storage battery.

[0047] The embodiment of the present application provides an energy storage container, including a thermal management system in the above embodiment. With such a configuration, when heating in an extremely low temperature environment, the refrigerant flowing out of the first heat exchanger 7 and flowing to the inlet of the compressor 1 first passes through the third heat exchanger 6 for heat exchange and temperature increase, and then mixes and heats up with the high-temperature and high-pressure gaseous refrigerant flowing out of the outlet of the compressor 1, so as to replace the role of the second heat exchanger 10 in evaporating and absorbing heat. By making all the heat sources in the refrigerant main circuit come from the power of the compressor 1 itself, the problem of slow heat exchange efficiency in an extremely low temperature environment can be solved.

[0048] The basic principles of the present application are described above in conjunction with specific embodiments. However, it should be noted that the advantages, strengths, effects, etc. mentioned in the present application are only examples and not limitations, and it cannot be considered that these advantages, strengths, effects, etc. are required by each embodiment of the present application. In addition, the specific details disclosed above are only for the purpose of illustration and ease of understanding, not for limitation, and the above details do not limit the present application to being implemented by adopting the above specific details.

[0049] The block diagrams of the devices, apparatuses, equipment, and systems involved in this application are only illustrative examples and are not intended to require or imply that they must be connected, arranged, and configured in the manner shown in the block diagram. As will be appreciated by those skilled in the art, these devices, apparatuses, equipment, and systems can be connected, arranged, and configured in any manner. Words such as "including", "comprising", "having", etc. are open words, referring to "including but not limited to", and can be used interchangeably with them. The words "or" and "and" used here refer to the words "and / or" and can be used interchangeably with them, unless the context clearly indicates otherwise. The words "such as" used here refer to the phrase "such as but not limited to", and can be used interchangeably with them.

[0050] It should also be noted that in the apparatus, device and method of the present application, each component or each step can be decomposed and / or recombined. Such decomposition and / or recombination should be regarded as equivalent solutions of the present application.

[0051] The above description of the disclosed aspects is provided to enable any person skilled in the art to make or use the present application. Various modifications to these aspects will be readily apparent to those skilled in the art, and the general principles defined herein may be applied to other aspects without departing from the scope of the present application. Therefore, the present application is not intended to be limited to the aspects shown herein, but rather to 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 the present application are only used to more clearly explain the technical solutions and cannot be used to limit the scope of protection of the present application.

[0053] The above description has been given for the purpose of illustration and description. In addition, this description is not intended to limit the embodiments of the present application to the forms disclosed herein. Although multiple example aspects and embodiments have been discussed above, those skilled in the art will recognize certain variations, modifications, changes, additions and sub-combinations thereof.

Claims

1. A thermal management system, characterized in that: Used to exchange heat for multiple batteries in an energy storage system, including: A refrigerant main circuit comprises a compressor, a first heat exchanger, a second heat exchanger and a third heat exchanger, wherein the third heat exchanger comprises a first heat exchange portion and a second heat exchange portion for exchanging heat with the first heat exchange portion, the inlet of the compressor is connected to the second heat exchanger through the first heat exchange portion, and the outlet of the compressor is connected to the first heat exchanger through the second heat exchange portion, 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, connected to an inlet and an outlet of the second heat exchanger, respectively, so that the refrigerant flowing out of the first heat exchanger flows to the first heat exchange part; The second refrigerant bypass is connected to the inlet and outlet of the compressor respectively, so that the refrigerant flowing out of the compressor is mixed with the refrigerant flowing out of the first heat exchange part.

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

3. The thermal management system according to claim 1, characterized in that: The inlet and the outlet of the compressor are respectively provided with a first temperature sensor and a second temperature sensor.

4. The thermal management system according to claim 1, characterized in that: A liquid storage device and a dryer are sequentially arranged 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: A plurality of the first heat exchangers are provided and are connected in parallel between the second heat exchange part and the second heat exchanger.

6. The thermal management system according to claim 1, characterized in that: The first refrigerant bypass has a first valve component to adjust the refrigerant flow of the first refrigerant bypass.

7. The thermal management system according to claim 6, characterized in that: The second refrigerant bypass has a second valve component to adjust the refrigerant flow rate of the second refrigerant bypass.

8. The thermal management system according to claim 7, characterized in that: A third valve is provided between the outlet of the compressor and the second heat exchange part to adjust the flow rate of the refrigerant flowing to the second heat exchange part.

9. The thermal management system according to claim 1, characterized in that: It includes a multi-way valve, wherein the first interface and the second interface of the multi-way valve are connected to the outlet of the compressor and the first heat exchange part respectively, and the third interface and the fourth interface of the multi-way valve are connected to the inlet of the compressor and the second heat exchange part respectively. In different modes, different interfaces among the first interface, the second interface, the third interface and the fourth interface are connected in pairs.

10. An energy storage container, characterized in that: The invention comprises a thermal management system as claimed in any one of claims 1 to 9.

11. A control method for a thermal management system, based on the thermal management system according to any one of claims 1 to 9, comprising: In the heating state, determine whether the ambient temperature is lower than the preset value; If so, the first valve is controlled to open so that the refrigerant of the first heat exchanger flows to the inlet of the compressor through the second refrigerant bypass and the first heat exchange part, and the second valve is controlled to open so that the refrigerant of the compressor is diverted to the inlet of the compressor through the first refrigerant bypass.

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