Thermal management system, energy storage system and photovoltaic energy storage system

Abstract

This application discloses a thermal management system, an energy storage system, and a photovoltaic energy storage system, belonging to the field of energy storage thermal management technology. The thermal management system includes: a first refrigerant main circuit, comprising a compressor and a gas-liquid separator; a second refrigerant main circuit, adapted to be connected to the first refrigerant main circuit, and comprising a first heat exchanger, a first path of a subcooler, a first expansion valve, and a second heat exchanger connected in sequence, the second heat exchanger being used for heat exchange with the energy storage battery of the energy storage system; and a bypass branch, comprising a second expansion valve and a second path of a subcooler, the inlet of the bypass branch being connected between the first heat exchanger and the first path of the subcooler, and the outlet of the bypass branch being connected between the second heat exchanger and the gas-liquid separator. Through the above-mentioned subcooler and bypass branch configuration, the subcooling degree of the refrigerant is effectively improved, the gas-liquid two-phase state maintenance time of the refrigerant in the second heat exchanger is extended, and the temperature uniformity of the energy storage battery is significantly improved.

Description

Technical Field

[0001] This application belongs to the field of energy storage thermal management technology, and particularly relates to a thermal management system, an energy storage system, and a photovoltaic energy storage system. Background Technology

[0002] In recent years, with the large-scale grid connection of new energy power generation, the installed capacity of electrochemical energy storage systems in the power grid has increased rapidly. Energy storage batteries generate a large amount of heat during charging and discharging. If this heat cannot be dissipated in time, it will cause the battery temperature to rise, leading to safety problems such as capacity decay, shortened lifespan, and even thermal runaway. Therefore, an efficient and reliable thermal management system has become crucial for the safe operation of energy storage systems.

[0003] Currently, commonly used thermal management solutions mainly include air cooling and liquid cooling. Air cooling systems have a simple structure but low heat exchange efficiency and large temperature differences. Liquid cooling systems, while having higher heat exchange efficiency, suffer from drawbacks such as high power consumption of the circulating pump and a high risk of leakage. Furthermore, when the ambient temperature is high or the heat load is large, the evaporator outlet is prone to excessive superheat and excessive refrigerant dryness, resulting in poorer cooling for cells closer to the outlet and significant temperature differences between cells at different locations within the energy storage battery. Utility Model Content

[0004] This application aims to address at least one of the technical problems existing in the prior art. To this end, this application proposes a thermal management system, an energy storage system, and a photovoltaic energy storage system, which improves the subcooling of the refrigerant, prolongs the maintenance time of the gas-liquid two-phase state of the refrigerant in the second heat exchanger, and significantly improves the temperature uniformity of the energy storage battery.

[0005] In a first aspect, this application provides a thermal management system for use in an energy storage system, comprising:

[0006] The first refrigerant main circuit includes the compressor and the gas-liquid separator;

[0007] The second refrigerant main circuit is adapted to be connected to the first refrigerant main circuit, and includes a first heat exchanger, a first circuit of a subcooler, a first expansion valve and a second heat exchanger connected in sequence. The second heat exchanger is used to exchange heat with the energy storage battery of the energy storage system.

[0008] The bypass branch includes a second expansion valve and a second path of the subcooler. The inlet of the bypass branch is connected between the first heat exchanger and the first path of the subcooler, and the outlet of the bypass branch is connected between the second heat exchanger and the gas-liquid separator.

[0009] According to the thermal management system of this application, by setting up the aforementioned subcooler and bypass branch, the second expansion valve is used to throttle and cool part of the refrigerant, allowing it to enter the second path of the subcooler for secondary subcooling of the refrigerant in the first path of the subcooler. This effectively increases the subcooling degree of the refrigerant, resulting in a higher liquid proportion in the refrigerant entering the second heat exchanger after throttling by the first expansion valve. This provides more usable liquid refrigerant for the evaporation process, thereby extending the maintenance time of the gas-liquid two-phase state of the refrigerant in the second heat exchanger. This effectively alleviates the premature complete evaporation of the refrigerant, ensuring that there is still sufficient liquid refrigerant at the outlet of the second heat exchanger for evaporation and heat absorption. This significantly improves the temperature uniformity of the energy storage battery, alleviates the situation where the cell temperature is higher closer to the outlet of the second heat exchanger, and thus extends the service life of the energy storage battery, improving the reliability and stability of the energy storage system.

[0010] According to one embodiment of this application, the thermal management system further includes:

[0011] The four-way valve includes a first to a fourth valve port, the first valve port being connected to the compressor, the second valve port being connected to the gas-liquid separator, the third valve port being connected to the first heat exchanger, and the fourth valve port being connected to the second heat exchanger.

[0012] According to one embodiment of this application, the thermal management system further includes:

[0013] A precooler, the inlet of which is connected to the fourth valve port, and the outlet of which is connected to the second heat exchanger.

[0014] According to the thermal management system of this application, the precooler cools the exhaust gas to near the saturation temperature to form a two-phase gas-liquid refrigerant. The latent heat is used to heat the energy storage battery, thereby significantly improving the cell temperature uniformity in the heating mode and reducing local overheating of the energy storage battery, thus reducing the risk of local thermal runaway of the energy storage battery. At the same time, in the cooling mode, no refrigerant passes through the precooler, so it does not affect the original subcooling design. In the heating mode, the precooler works in conjunction with the four-way valve, without the need for an additional switching valve. In addition, the precooler reduces the exhaust temperature and reduces the condensing pressure of the second heat exchanger, thereby relieving the load on the compressor 111.

[0015] According to one embodiment of this application, the thermal management system further includes:

[0016] The first fan is used to drive the airflow in the first airflow. The first airflow is connected to the gas flow channel of the first heat exchanger and the gas flow channel of the precooler.

[0017] According to one embodiment of this application, the thermal management system further includes:

[0018] The second fan is used to drive the airflow in the second air duct, and the second air duct is connected to the gas flow channel of the first heat exchanger.

[0019] A third fan is provided, and the thermal management system forms a third air duct. The third fan drives the airflow within the third air duct. The third air duct is connected to the gas flow channel of the precooler and is shared with the gas flow channels of the second air duct and the first heat exchanger. According to one embodiment of this application, the thermal management system further includes:

[0020] The regenerator has its first inlet connected to the second heat exchanger, its first outlet connected to the fourth valve port, its second outlet connected between the first heat exchanger and the subcooler, and the inlet of the bypass branch connected between the first heat exchanger and the first outlet of the subcooler, and the outlet of the bypass branch connected between the outlet of the regenerator and the fourth valve port.

[0021] According to one embodiment of this application, the gas-liquid separator has a heating section.

[0022] According to one embodiment of this application, the gas-liquid separator includes:

[0023] First shell;

[0024] The second shell is disposed inside the first shell, and a first heat storage material is disposed between the first shell and the second shell;

[0025] The gas distribution coil is connected to the second housing;

[0026] The first heat exchange coil, the heating part and the first heat exchange coil are both located between the first shell and the second shell, and are both wrapped by the first heat storage material. The outlet of the first heat exchange coil is connected to the inlet of the gas separation coil.

[0027] According to one embodiment of this application, the thermal management system further includes:

[0028] A heating device is connected in parallel to the first heat exchanger.

[0029] According to one embodiment of this application, the heating device includes:

[0030] The shell contains a second heat storage material inside;

[0031] The heating element and the second heat exchange coil are separately disposed within the housing and are both wrapped by the second heat storage material.

[0032] Secondly, this application provides an energy storage system, which includes:

[0033] Energy storage batteries;

[0034] The thermal management system described in any of the above embodiments is electrically connected to the energy storage battery.

[0035] According to the energy storage system of this application, by setting up the aforementioned thermal management system, a portion of the refrigerant is throttled and cooled using a second expansion valve, allowing it to enter the second path of the subcooler for secondary subcooling of the refrigerant in the first path of the subcooler. This effectively increases the subcooling degree of the refrigerant, resulting in a higher liquid proportion in the refrigerant entering the second heat exchanger after throttling through the first expansion valve. This provides more usable liquid refrigerant for the evaporation process, thereby extending the duration of the gas-liquid two-phase state of the refrigerant in the second heat exchanger. This effectively alleviates the premature complete evaporation of the refrigerant, ensuring that there is still sufficient liquid refrigerant at the outlet of the second heat exchanger for evaporation and heat absorption. This significantly improves the temperature uniformity of the energy storage battery, alleviates the situation where the cell temperature is higher closer to the outlet of the second heat exchanger, and thus extends the service life of the energy storage battery, improving the reliability and stability of the energy storage system.

[0036] Thirdly, this application provides a photovoltaic energy storage system, which includes:

[0037] Such as the energy storage system mentioned above;

[0038] A photovoltaic power generation system, wherein the photovoltaic power generation system is used to supply power to the energy storage system.

[0039] According to the photovoltaic energy storage system of this application, by setting up the energy storage system, a portion of the refrigerant is throttled and cooled using a second expansion valve, allowing it to enter the second path of the subcooler for secondary subcooling of the refrigerant in the first path of the subcooler. This effectively increases the subcooling degree of the refrigerant, resulting in a higher liquid proportion in the refrigerant entering the second heat exchanger after throttling through the first expansion valve. This provides more usable liquid refrigerant for the evaporation process, thereby extending the maintenance time of the gas-liquid two-phase state of the refrigerant in the second heat exchanger. This effectively alleviates the premature complete evaporation of the refrigerant, ensuring that there is still sufficient liquid refrigerant at the outlet of the second heat exchanger for evaporation and heat absorption. This significantly improves the temperature uniformity of the energy storage battery, alleviates the situation where the cell temperature is higher closer to the outlet of the second heat exchanger, and thus extends the service life of the energy storage battery, improving the reliability and stability of the energy storage system.

[0040] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0041] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0042] Figure 1 This is one of the structural schematic diagrams of the thermal management system provided in the embodiments of this application;

[0043] Figure 2 yes Figure 1 A schematic diagram of the refrigerant flow in the cooling mode of the thermal management system shown.

[0044] Figure 3 yes Figure 1 A schematic diagram of the refrigerant flow direction in the heating mode of the thermal management system shown.

[0045] Figure 4 yes Figure 1 A schematic diagram of the refrigerant flow direction in the self-circulation mode of the thermal management system shown;

[0046] Figure 5 yes Figure 1 A schematic diagram of the refrigerant flow in the defrosting mode of the thermal management system shown.

[0047] Figure 6 This is a second schematic diagram of the structure of the thermal management system provided in the embodiments of this application;

[0048] Figure 7 yes Figure 6 A schematic diagram of the refrigerant flow in the cooling mode of the thermal management system shown.

[0049] Figure 8 yes Figure 6 One of the schematic diagrams showing the refrigerant flow direction of the thermal management system in heating mode;

[0050] Figure 9 yes Figure 6 The second schematic diagram of the refrigerant flow direction of the thermal management system in heating mode;

[0051] Figure 10 yes Figure 6 A schematic diagram of the refrigerant flow direction in the self-circulation mode of the thermal management system shown;

[0052] Figure 11 yes Figure 6 One of the schematic diagrams showing the refrigerant flow direction of the thermal management system in defrost mode;

[0053] Figure 12 yes Figure 6 The second schematic diagram of the refrigerant flow direction of the thermal management system in defrost mode;

[0054] Figure 13 This is the third schematic diagram of the thermal management system provided in the embodiments of this application;

[0055] Figure 14 yes Figure 13A schematic diagram of the refrigerant flow in the cooling mode of the thermal management system shown.

[0056] Figure 15 yes Figure 13 A schematic diagram of the refrigerant flow direction in the heating mode of the thermal management system shown.

[0057] Figure 16 yes Figure 13 A schematic diagram of the refrigerant flow direction in the self-circulation mode of the thermal management system shown;

[0058] Figure 17 yes Figure 13 One of the schematic diagrams showing the refrigerant flow direction of the thermal management system in defrost mode;

[0059] Figure 18 yes Figure 13 The second schematic diagram of the refrigerant flow direction of the thermal management system in defrost mode;

[0060] Figure 19 This is the fourth schematic diagram of the thermal management system provided in the embodiments of this application;

[0061] Figure 20 yes Figure 19 A schematic diagram of the refrigerant flow in the cooling mode of the thermal management system shown.

[0062] Figure 21 yes Figure 19 A schematic diagram of the refrigerant flow direction in the heating mode of the thermal management system shown.

[0063] Figure 22 yes Figure 19 A schematic diagram of the refrigerant flow direction in the self-circulation mode of the thermal management system shown;

[0064] Figure 23 yes Figure 19 A schematic diagram of the refrigerant flow in the defrosting mode of the thermal management system shown.

[0065] Figure 24 This is one of the schematic diagrams of the heat dissipation airflow of the first heat exchanger and precooler provided in the embodiments of this application;

[0066] Figure 25 This is the second schematic diagram of the heat dissipation airflow direction of the first heat exchanger and precooler provided in the embodiments of this application;

[0067] Figure 26 This is a schematic diagram of the gas-liquid separator provided in the embodiments of this application;

[0068] Figure 27 This is a structural perspective view of the gas-liquid separator provided in the embodiments of this application;

[0069] Figure 28This is a schematic diagram of the heating device provided in the embodiments of this application;

[0070] Figure 29 This is a structural perspective view of the heating device provided in the embodiments of this application.

[0071] Figure label:

[0072] Thermal Management System 10;

[0073] First refrigerant main circuit 11, compressor 111, gas-liquid separator 112, first shell 1121, second shell 1122, gas distribution coil 1123, heating unit 1124, first heat exchange coil 1125, first heat storage material 1126, connecting pipe 1127, first temperature sensor 1128.

[0074] Second refrigerant main line 12a, first expansion valve 12a1, first heat exchanger 12a2, second heat exchanger 12a3, dryer filter 12a4, liquid receiver 12a5, liquid distributor 12a6, capillary tube 12a7, shut-off valve 12a8.

[0075] Bypass branch 12b, second expansion valve 12b1, first check valve 12b2;

[0076] Subcooler 124, subcooler first path 124a, subcooler second path 124b;

[0077] Four-way valve 13, first valve port 131, second valve port 132, third valve port 133, fourth valve port 134;

[0078] Precooler 141, second check valve 142, regenerator 143, first path of regenerator 143a, second path of regenerator 143b, third check valve 144.

[0079] First fan 151, second fan 152, third fan 153;

[0080] First air duct 161, second air duct 162, third air duct 163;

[0081] Heating device 17, housing 171, heating element 172, second heat exchange coil 173, second heat storage material 174, second temperature sensor 175;

[0082] First solenoid valve 181, second solenoid valve 182, third solenoid valve 183. Detailed Implementation

[0083] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0084] This application discloses a thermal management system 10, which is applied to an energy storage system.

[0085] The following is for reference. Figures 1-29 A thermal management system 10 according to an embodiment of this application is described.

[0086] In some embodiments, such as Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the thermal management system 10 includes: a first refrigerant main line 11, a second refrigerant main line 12a, and a bypass branch line 12b.

[0087] The first refrigerant main circuit 11 includes a compressor 111 and a gas-liquid separator 112; the second refrigerant main circuit 12a is adapted to be connected to the first refrigerant main circuit 11, and the second refrigerant main circuit 12a includes a first heat exchanger 12a2, a first path 124a of a subcooler 124, a first expansion valve 12a1 and a second heat exchanger 12a3 connected in sequence, the second heat exchanger 12a3 being used for heat exchange with the energy storage battery of the energy storage system; the bypass branch 12b includes a second expansion valve 12b1 and a second path 124b of a subcooler 124, the inlet of the bypass branch 12b is connected between the first heat exchanger 12a2 and the first path 124a of the subcooler 124, and the outlet of the bypass branch 12b is connected between the second heat exchanger 12a3 and the gas-liquid separator 112.

[0088] like Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the second refrigerant main circuit 12a may further include a dryer filter 12a4 and a receiver 12a5. The dryer filter 12a4 can be connected in series at the outlet end of the first heat exchanger 12a2 to adsorb moisture and impurities in the refrigerant. The receiver 12a5 can be connected in series between the first expansion valve 12a1 and the second heat exchanger 12a3 to stabilize the refrigerant charge required for the system circulation. In this way, the first refrigerant circuit and the second refrigerant circuit can be connected end to end to form a complete refrigerant cycle.

[0089] It should be noted that, as Figure 1 , Figure 6 , Figure 13 and Figure 19As shown, the energy storage battery is typically distributed vertically in multiple layers, with multiple second heat exchangers 12a3 connected in parallel to exchange heat with each of the multiple layers of batteries. To achieve uniform distribution of the refrigerant in the multiple second heat exchangers 12a3, the second refrigerant main line 12a may also include a distributor 12a6 and a capillary tube 12a7. The distributor 12a6 can be located at the inlet and outlet ends of the second heat exchangers 12a3, and the capillary tube 12a7 can be located between the distributor 12a6 and the second heat exchangers 12a3 for further throttling after the first expansion valve 12a1, while also facilitating adjustment of the resistance at the inlet and outlet ends of each second heat exchanger 12a3.

[0090] The liquid separator 12a6 can be of various types, such as pressure drop type, conical type, venturi type, venturi tube type, reflective type, socket type, impeller type or mixed flow guiding structure, etc., and the embodiments of this application do not limit this.

[0091] like Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the bypass branch 12b is a branch line for the refrigerant circulation consisting of the first refrigerant circuit and the second refrigerant circuit, which is located after the first heat exchanger 12a2 and before the first expansion valve 12a1. The bypass branch 12b may also include a first check valve 12b2, which only allows the refrigerant to flow unidirectionally from the second expansion valve 12b1 to the second path 124b of the subcooler 124 in the bypass branch 12b.

[0092] In actual implementation, such as Figure 2 , Figure 7 , Figure 14 and Figure 20As shown, when the thermal management system 10 starts the refrigeration cycle, the compressor 111 begins to work, drawing in and compressing the low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gas. The high-temperature, high-pressure refrigerant enters the first heat exchanger 12a2, where it exchanges heat with the external environment, releasing some heat and lowering its temperature. The refrigerant exiting the first heat exchanger 12a2 is divided into two paths: one enters the first path 124a of the subcooler 124, and the other enters the bypass branch 12b. The refrigerant entering the bypass branch 12b is throttled and depressurized by the second expansion valve 12b1, further reducing its temperature, and then enters the second path 124b of the subcooler 124. In the subcooler 124, the low-temperature refrigerant in the bypass branch 12b exchanges heat with the refrigerant in the first path 124a of the subcooler 124, performing secondary subcooling on the refrigerant in the first path 124a of the subcooler 124, increasing its subcooling degree. After being cooled by the subcooler 124, the refrigerant flows out from the first channel 124a of the subcooler 124 and enters the first expansion valve 12a1 for throttling and pressure reduction, becoming a low-temperature, low-pressure liquid or gas-liquid mixture of refrigerant. It then enters the second heat exchanger 12a3. In the second heat exchanger 12a3, the refrigerant exchanges heat with the energy storage battery, absorbing heat from the battery and evaporating, thus cooling the energy storage battery. The evaporated gas-liquid mixture flows out from the second heat exchanger 12a3 and enters the gas-liquid separator 112 for separation. The separated gaseous refrigerant returns to the compressor 111 to begin the next cycle, while the liquid refrigerant remains at the bottom of the gas-liquid separator 112 to prevent it from entering the compressor 111 and causing damage.

[0093] Understandably, since the refrigerant in bypass branch 12b is throttled and cooled by the second expansion valve 12b1 before entering the second branch 124b of subcooler 124, it exchanges heat with the refrigerant in the first branch 124a of subcooler 124, thus providing secondary subcooling to the refrigerant in the first branch 124a of subcooler 124. This design significantly improves the subcooling degree of the refrigerant, ensuring that the refrigerant is at a lower temperature and in a higher subcooled state before entering the first expansion valve 12a1. Due to the increased subcooling degree, the flash gas after throttling by the first expansion valve 12a1 is reduced, increasing the proportion of liquid in the refrigerant entering the second heat exchanger 12a3, i.e., lower dryness. More liquid refrigerant means that more liquid substances can absorb heat during the evaporation process in the second heat exchanger 12a3, providing more usable liquid refrigerant for the evaporation process. The presence of more liquid refrigerant allows it to remain in a gas-liquid two-phase state for a longer period within the second heat exchanger 12a3, minimizing the possibility of the refrigerant completely evaporating into pure superheated gas before reaching the outlet of the second heat exchanger 12a3. By extending the duration of the gas-liquid two-phase state, the second heat exchanger 12a3 can effectively exchange heat along its entire length, enabling more uniform cooling of the energy storage battery. This improves the overall heat exchange efficiency of the thermal management system 10, helps maintain the energy storage battery within a suitable operating temperature range, enhances the reliability and stability of the energy storage system, and extends the battery's lifespan.

[0094] The thermal management system 10 provided in this application embodiment, through the setting of the supercooler 124 and the bypass branch 12b, uses the second expansion valve 12b1 to throttle and cool part of the refrigerant, so that it enters the second path 124b of the supercooler 124 to perform secondary subcooling on the refrigerant in the first path 124a of the supercooler 124. This effectively improves the subcooling degree of the refrigerant, so that the proportion of liquid in the refrigerant entering the second heat exchanger 12a3 after throttling by the first expansion valve 12a1 is higher. This provides more usable liquid refrigerant for the evaporation process, thereby extending the maintenance time of the gas-liquid two-phase state of the refrigerant in the second heat exchanger 12a3. This effectively alleviates the premature complete evaporation of the refrigerant, and ensures that there is still enough liquid refrigerant at the outlet of the second heat exchanger 12a3 for evaporation and heat absorption. This significantly improves the temperature uniformity of the energy storage battery, alleviates the situation that the cell temperature is higher closer to the outlet of the second heat exchanger 12a3, and thus extends the service life of the energy storage battery and improves the reliability and stability of the energy storage system.

[0095] In some embodiments, such as Figures 1-23 As shown, the thermal management system 10 also includes a four-way valve 13.

[0096] The four-way valve 13 includes a first valve port 131 to a fourth valve port 134. The first valve port 131 is connected to the compressor 111, the second valve port 132 is connected to the gas-liquid separator 112, the third valve port 133 is connected to the first heat exchanger 12a2, and the fourth valve port 134 is connected to the second heat exchanger 12a3.

[0097] In this embodiment, such as Figures 1-23 As shown, the four-way valve 13 is a reversing control valve with four ports. The four ports are respectively connected to the two ends of the first refrigerant main line 11 and the two ends of the second refrigerant main line 12a. The valve core can be driven by an electromagnetic coil to switch the refrigerant flow direction, realizing the switching between cooling mode and heating mode. Specifically, the first port 131 is connected to the compressor 111 and is the channel for refrigerant to enter and exit the compressor 111; the second port 132 is connected to the gas-liquid separator 112 to ensure that the refrigerant returning to the compressor 111 has passed through gas-liquid separation; the third port 133 is connected to the first heat exchanger 12a2, and the fourth port 134 is connected to the second heat exchanger 12a3. By changing the position of the valve core inside the four-way valve 13, the flow direction of the refrigerant can be changed, thereby realizing the interchange of the functions of the first heat exchanger 12a2 and the second heat exchanger 12a3. That is, when cooling, the first heat exchanger 12a2 condenses the refrigerant and the second heat exchanger 12a3 evaporates the refrigerant; when heating, the first heat exchanger 12a2 evaporates the refrigerant and the second heat exchanger 12a3 condenses the refrigerant, so as to achieve the purpose of switching between cooling and heating modes.

[0098] The thermal management system 10 provided in this embodiment, through the aforementioned four-way valve 13, is no longer limited to a single cooling or heating function. Instead, it can flexibly switch between the two modes according to the actual needs of the energy storage system, enabling the energy storage battery to operate within a suitable temperature range and improving the adaptability of the energy storage system to different environmental conditions. Simultaneously, it eliminates the need for separate refrigerant circulation loops and heat exchangers for the two functions, greatly simplifying the system structure, reducing the number of components and piping connections, lowering system complexity and cost, and also facilitating system installation, maintenance, and repair.

[0099] In some embodiments, such as Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the thermal management system 10 also includes a precooler 141.

[0100] The inlet of the precooler 141 is connected to the fourth valve port 134, and the outlet of the precooler 141 is connected to the second heat exchanger 12a3.

[0101] The precooler 141 can be a plate heat exchanger, a microchannel heat exchanger, or a finned heat exchanger, etc., and this application embodiment does not limit this.

[0102] It should be noted that in heating mode, the high-temperature and high-pressure gaseous refrigerant discharged by the compressor 111 directly enters the second heat exchanger 12a3 to heat the energy storage battery. Due to the high sensible heat temperature of the refrigerant and its uneven distribution on the surface of the energy storage battery, the cells at different locations of the battery will have large differences in heating and obvious temperature gradients. Specifically, the high sensible heat will cause the cells near the inlet to overheat, while the outlet side will not be heated enough, thus affecting the temperature uniformity of the cells.

[0103] In this embodiment, such as Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the precooler 141 is connected in series between the fourth valve port 134 of the four-way valve 13 and the second heat exchanger 12a3. A second one-way valve 142 can be installed on the branch where the precooler 141 is located. The second one-way valve 142 only allows the refrigerant to flow in one direction from the compressor 111 to the precooler 141. In the heating mode, the compressor 111 discharges high-temperature and high-pressure gaseous refrigerant containing a large amount of sensible heat. The refrigerant flows into the four-way valve 13 from the first valve port 131 and flows out from the fourth valve port 134. It first passes through the precooler 141. The precooler 141 cools the high-temperature and high-pressure gaseous refrigerant containing a large amount of sensible heat, causing it to partially condense into a liquid state, forming a gas-liquid two-phase state before entering the second heat exchanger 12a3. The second heat exchanger 12a3 mainly heats the energy storage battery through the latent heat of refrigerant condensation (i.e., phase change heat).

[0104] Understandably, on the one hand, the precooler 141 eliminates the sensible heat in the refrigerant, ensuring that the refrigerant entering the second heat exchanger 12a3 is in a gas-liquid two-phase state. In this state, the refrigerant releases latent heat in the second heat exchanger 12a3 for heating. During the latent heat release process, the temperature remains relatively constant, allowing the cells in various parts of the battery to be heated in a more uniform temperature environment, effectively improving the temperature uniformity of the cells and ensuring the performance and lifespan of the energy storage battery. On the other hand, the presence of the precooler 141 enables the thermal management system 10 to more precisely control the state of the refrigerant entering the second heat exchanger 12a3 in heating mode. By adjusting the cooling intensity of the precooler 141, such as adjusting the fan speed of an air-cooled precooler 141 or adjusting the cooling water flow rate of a water-cooled precooler 141, the gas-liquid ratio of the refrigerant can be precisely controlled, thereby better matching the heating requirements of the energy storage battery. This helps improve the overall performance of the thermal management system 10, enabling the energy storage system to operate stably and efficiently under different operating conditions. Furthermore, the heating requirements and refrigerant state requirements of energy storage systems vary under different ambient temperatures and usage scenarios. The precooler 141 can flexibly adjust its cooling effect according to actual conditions, enabling the thermal management system 10 to adapt to various complex environmental conditions and usage scenarios. For example, in extremely cold environments, the cooling capacity of the precooler 141 can be appropriately reduced to ensure that the refrigerant entering the second heat exchanger 12a3 has sufficient heat to heat the battery; in mild environments, cooling can be enhanced to maintain the uniformity of the battery cells. This adaptability gives the thermal management system 10 a wider range of applications.

[0105] The thermal management system 10 provided in this application embodiment, through the setting of the precooler 141, cools the exhaust gas to near the saturation temperature to form a gas-liquid two-phase refrigerant, and uses latent heat to heat the energy storage battery, thereby significantly improving the cell temperature uniformity in the heating mode and reducing local overheating of the energy storage battery, reducing the risk of local thermal runaway of the energy storage battery. At the same time, in the cooling mode, no refrigerant passes through the precooler 141, which does not affect the original overcooling design. In the heating mode, the precooler 141 works in conjunction with the four-way valve 13, without the need for an additional switching valve. In addition, the precooler 141 reduces the exhaust temperature and reduces the condensing pressure of the second heat exchanger 12a3, thereby relieving the load on the compressor 111.

[0106] In some embodiments, such as Figure 13 , Figure 19 and Figure 24 As shown, the thermal management system 10 also includes a first fan 151.

[0107] The thermal management system 10 forms a first air duct 161, and a first fan 151 is used to drive the airflow in the first air duct 161. The first air duct 161 is connected to the gas flow channel of the first heat exchanger 12a2 and the gas flow channel of the precooler 141.

[0108] The first fan 151 can be set to one or more, where multiple means two or more.

[0109] For example, in some embodiments, such as Figure 24 As shown, two first fans 151 are installed.

[0110] In this embodiment, such as Figure 24 As shown, the first fan 151 rotates to drive the airflow in the first air duct 161 to flow rapidly. The airflow can first flow through the gas flow channel of the precooler 141, then through the gas flow channel of the first heat exchanger 12a2, and finally be discharged from the first air duct 161.

[0111] In other embodiments, the first fan 151 rotates to drive the airflow in the first air duct 161 to flow rapidly. The airflow can first flow through the gas flow channel of the first heat exchanger 12a2, then through the gas flow channel of the precooler 141, and finally be discharged from the first air duct 161.

[0112] In some other embodiments, the first air duct 161 splits into two branches at the fan outlet, connecting the gas flow channels of the first heat exchanger 12a2 and the precooler 141 respectively, and then merges at the end before being discharged. The airflow ratio of the two branches can be adjusted by a valve; for example, the airflow of the first heat exchanger 12a2 branch is increased during cooling, and the airflow of the precooler 141 branch is increased during heating, which is suitable for scenarios where the heat dissipation requirements of the two branches differ greatly.

[0113] The thermal management system 10 provided in this application embodiment uses a design where the first heat exchanger 12a2 and the precooler 141 share the first fan 151 and the first air duct 161 for heat dissipation. This eliminates the need for separate fans and air ducts for each component, reducing the number of fans and construction costs, saving internal space, making the thermal management system 10 more compact, reducing energy consumption, and achieving energy-saving operation. Furthermore, control only requires unified adjustment of the first fan 151. This simplifies the control logic and control system, thereby reducing control complexity and cost.

[0114] In some embodiments, such as Figure 1 , Figure 6 and Figure 25 As shown, the thermal management system 10 also includes a second fan 152 and a third fan 153.

[0115] The thermal management system 10 forms a second air duct 162, and a second fan 152 is used to drive the airflow within the second air duct 162. The second air duct 162 is connected to the gas flow channel of the first heat exchanger 12a2. The thermal management system 10 forms a third air duct 163, and a third fan 153 is used to drive the airflow within the third air duct 163. The third air duct 163 is connected to the gas flow channel of the precooler 141 and is separated from both the second air duct 162 and the gas flow channel of the first heat exchanger 12a2.

[0116] Among them, the second fan 152 and the third fan 153 can be set one or more, where multiple means two or more.

[0117] For example, in some embodiments, such as Figure 25 As shown, two second fans 152 are provided, and one third fan 153 is provided.

[0118] In this embodiment, such as Figure 25 As shown, the first heat exchanger 12a2 can be installed inside the casing 171 of the unit, and the second fan 152 drives the airflow into the second air duct 162 inside the casing 171 of the unit; the precooler 141 can be installed outside the casing 171 of the unit, forming a separate third air duct 163 on the outside, and is equipped with an independent third fan 153.

[0119] The thermal management system 10 provided in this application embodiment, through the design of independent heat dissipation for the first heat exchanger 12a2 and the precooler 141, can precisely control the speed and airflow of the second fan 152 and the third fan 153 according to the actual working state and heat dissipation requirements of the first heat exchanger 12a2 and the precooler 141, so that each component operates under the best heat dissipation conditions, thereby improving the heat dissipation accuracy and efficiency of the entire thermal management system 10. At the same time, the third air duct 163 is separated from the second air duct 162 and the gas flow channel of the first heat exchanger 12a2, effectively avoiding mutual interference of airflow when different components dissipate heat, thereby improving the stability and reliability of heat dissipation.

[0120] In some embodiments, such as Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the thermal management system 10 also includes a regenerator 143.

[0121] The inlet of the first path 143a of the regenerator 143 is connected to the second heat exchanger 12a3, the outlet of the first path 143a of the regenerator 143 is connected to the fourth valve port 134, the second path 143b of the regenerator 143 is connected between the first heat exchanger 12a2 and the subcooler 124, and the inlet of the bypass branch 12b is connected between the first heat exchanger 12a2 and the first path 124a of the subcooler 124, and the outlet of the bypass branch 12b is connected between the outlet of the regenerator 143 and the fourth valve port 134.

[0122] The regenerator 143 can be a plate heat exchanger, a shell-and-tube heat exchanger or other types of heat exchangers, and this application embodiment does not limit this.

[0123] In actual implementation, such as Figure 1 , Figure 2 , Figure 6 , Figure 7 , Figure 13 , Figure 14 , Figure 19 and Figure 20 As shown, the precooler 141 is connected in parallel with the first path 143a of the regenerator 143. The first path 143a of the regenerator 143 is equipped with a third one-way valve 144, which only allows the refrigerant to flow unidirectionally from the second heat exchanger 12a3 to the first path 143a of the regenerator 143. In cooling mode, the refrigerant from the second heat exchanger 12a3 exchanges heat with the refrigerant flowing from the first heat exchanger 12a2 in the second path 143b of the regenerator 143. This heat exchange increases the subcooling of the refrigerant flowing from the first heat exchanger 12a2 in the second path 143b of the regenerator 143, enabling it to absorb heat from the battery cell more effectively, thereby improving the temperature distribution of the battery cell and enhancing its temperature uniformity. Meanwhile, the superheat of the refrigerant flowing from the second heat exchanger 12a3 in the first path 143a of the regenerator 143 increases, which means that the liquid component in the refrigerant decreases and the gaseous component increases. When this part of the refrigerant enters the suction port of the compressor 111 through the gas-liquid separator 112, it can effectively reduce the direct entry of liquid refrigerant into the compressor 111, thereby significantly reducing the occurrence of liquid slugging in the compressor 111.

[0124] Furthermore, in heating mode, the system's operating principle and refrigerant flow path differ from those in cooling mode. Based on the parallel connection of the precooler 141 and the first path 143a of the regenerator 143, the refrigerant is prevented from bypassing the first path 143a of the regenerator 143. This avoids unnecessary heat exchange and energy loss, allowing the refrigerant to flow along the optimal path in heating mode, thus improving heating efficiency. This allows for flexible system adjustments based on different operating modes, fully leveraging the performance advantages of the thermal management system 10 under various conditions.

[0125] The thermal management system 10 provided in this application embodiment, through the aforementioned configuration of the regenerator 143, further reduces the high-pressure refrigerant temperature in the second path 143b of the regenerator 143. After throttling by the first expansion valve 12a1, the proportion of liquid refrigerant is further increased, ensuring sufficient liquid refrigerant evaporation throughout the entire second heat exchanger 12a3, thereby minimizing the temperature gradient between multiple cells within the energy storage battery. Simultaneously, the refrigerant superheat in the first path 143a of the regenerator 143 increases, raising the proportion of gaseous refrigerant, thereby reducing the risk of liquid slugging in the compressor 111 and reducing the load on the gas-liquid separator 112, thus extending the service life of the compressor 111 and the gas-liquid separator 112.

[0126] In some embodiments, such as Figure 1 , Figure 19 , Figure 26 and Figure 27 As shown, the gas-liquid separator 112 has a heating section 1124.

[0127] The heating unit 1124 is a newly added component for heating on the gas-liquid separator 112. The heating unit 1124 can adopt a variety of heating methods, such as electric heating wire, PTC (Positive Temperature Coefficient) heater or heat pump waste heat utilization, etc. This application embodiment does not limit this.

[0128] The function of the heating unit 1124 is to heat the refrigerant in the gas-liquid separator 112 under specific operating conditions, thereby changing the temperature and state of the refrigerant to meet different operating requirements of the system.

[0129] In actual operation, under extremely cold conditions, the refrigerant temperature is low, resulting in insufficient suction superheat entering the compressor 111, which may lead to difficulty in starting the compressor 111 or unstable operation. With the gas-liquid separator 112 equipped with a heating element 1124, before starting the heating mode, the heating element 1124 can heat the refrigerant inside the gas-liquid separator 112, increasing the refrigerant temperature and the suction superheat of the compressor 111. This allows the compressor 111 to reach normal operating conditions in a shorter time, quickly starting the heating mode to heat the energy storage battery, thus improving the adaptability and starting performance of the thermal management system 10 in extremely cold environments.

[0130] In addition, the thermal management system 10 can also be configured with a defrost mode. In defrost mode, the heating unit 1124 heats the refrigerant in the gas-liquid separator 112, causing some of the liquid refrigerant to vaporize and increasing the amount of gaseous refrigerant, thereby increasing the refrigerant circulation rate. More refrigerant can remove the frost layer on the evaporator surface more quickly, improving the defrost speed and reducing the defrost time.

[0131] It should be noted that, as Figure 1 , Figure 6 , Figure 13 and Figure 19 As shown, the second refrigerant main line 12a also includes a shut-off valve 12a8. The shut-off valve 12a8 is located at the inlet and outlet of the second heat exchanger 12a3. In dehumidification mode, the shut-off valve 12a8 is closed so that the refrigerant does not flow through the second heat exchanger 12a3, thereby reducing the impact of the defrosting process on the temperature of the energy storage battery.

[0132] The thermal management system 10 provided in this application embodiment, through the structural design of integrating the heating unit 1124 into the gas-liquid separator 112, has several advantages. On the one hand, the heating unit 1124 can directly vaporize the liquid refrigerant, allowing the compressor 111 to draw in sufficient superheated gas, thus enabling rapid start-up heating in extremely cold environments and improving the system's environmental adaptability. On the other hand, when the defrosting effect is difficult to achieve as expected, the heating unit 1124 forces the evaporation of the liquid refrigerant accumulated in the gas-liquid separator 112, increasing the circulation flow of the gaseous refrigerant and enhancing the defrosting capability, thereby significantly shortening the defrosting time. Furthermore, the integration of the heating function and the gas-liquid separation function eliminates the need for installation space and piping connections for an independent heater, reducing the volume of the thermal management system 10 and thus improving the space utilization rate of the energy storage system.

[0133] In some embodiments, such as Figure 26 and Figure 27 As shown, the gas-liquid separator 112 includes: a first shell 1121, a second shell 1122, a gas separation coil 1123, and a first heat exchange coil 1125.

[0134] The second shell 1122 is disposed inside the first shell 1121, and a first heat storage material 1126 is disposed between the first shell 1121 and the second shell 1122; the gas distribution coil 1123 is connected inside the second shell 1122; the heating part 1124 and the first heat exchange coil 1125 are both disposed between the first shell 1121 and the second shell 1122, and are both wrapped by the first heat storage material 1126; the outlet of the first heat exchange coil 1125 is connected to the inlet of the gas distribution coil 1123.

[0135] The first shell 1121 serves as the outermost protective structure of the gas-liquid separator 112, and plays the role of accommodating internal components and protecting internal parts from the influence of the external environment.

[0136] The second shell 1122 is located inside the first shell 1121, providing a relatively independent and protected space for the gas separator coil 1123 and the internal gas-liquid separation process.

[0137] The gap between the first shell 1121 and the second shell 1122 is used to fill the first heat storage material 1126. The first heat storage material 1126 can absorb and store heat when the heating part 1124 is heated, and transfer the heat to the surrounding components, such as the first heat exchange coil 1125 and the gas distribution coil 1123, when needed, so as to stabilize the temperature and reduce heat loss.

[0138] The first heat storage material 1126 can be a liquid or a solid powder, and this application embodiment does not limit it.

[0139] Specifically, the first heat storage material 1126 may include, but is not limited to, paraffin-based phase change materials, inorganic hydrated salt phase change materials, aluminum powder or magnesium oxide powder, etc., and the embodiments of this application do not limit this.

[0140] The gas separator coil 1123 is housed inside the second shell 1122. The gas separator coil 1123 is a spiral or U-shaped coil, etc. The inlet of the gas separator coil 1123 is connected to the outlet of the first heat exchange coil 1125, and the outlet of the gas separator coil 1123 is connected to the suction port of the compressor 111.

[0141] When the refrigerant flows in the gas separator coil 1123, due to the pipe structure and flow characteristics, the gaseous and liquid refrigerant will gradually separate. The gaseous refrigerant continues to flow into the subsequent system, while the liquid refrigerant remains in the gas separator coil 1123 or sinks to the bottom of the gas-liquid separator 112.

[0142] The first heat exchange coil 1125 and the heating element 1124 are housed in the gap between the first shell 1121 and the second shell 1122. Both the first heat exchange coil 1125 and the heating element 1124 are in close contact with the first heat storage material 1126. The first heat exchange coil 1125 can adopt a serpentine or spiral layout, etc. The inlet of the first heat exchange coil 1125 is connected to the second valve port 132 of the four-way valve 13, and the outlet of the first heat exchange coil 1125 is connected to the inlet of the gas distribution coil 1123, which is the preheating channel before the refrigerant enters the gas distribution coil 1123.

[0143] In this embodiment, such as Figure 26 and Figure 27As shown, the refrigerant first flows into the first heat exchange coil 1125. In the first heat exchange coil 1125, the refrigerant directly contacts the heating element 1124 and the first heat storage material 1126 to exchange heat. Part of the heat generated by the heating element 1124 is directly transferred to the refrigerant in the first heat exchange coil 1125, causing the refrigerant temperature to rise. At the same time, the first heat storage material 1126 absorbs and stores the heat from the heating element 1124, and then slowly releases it to the refrigerant in the first heat exchange coil 1125, further improving the heating effect of the refrigerant. Since the outlet of the first heat exchange coil 1125 and the inlet of the gas distribution coil 1123 both face upwards, a curved connecting pipe 1127 is installed between them. The refrigerant, after initial heating, then flows into the gas distribution coil 1123 through the connecting pipe 1127. In the gas distribution coil 1123, it can further absorb heat transferred from the heating element 1124 through the second shell 1122 and heat released by the first heat storage material 1126, achieving secondary heating. This staged heating method allows the refrigerant to fully absorb heat throughout the entire flow process, resulting in more thorough heating.

[0144] It should be noted that, as Figure 26 and Figure 27 As shown, the gas-liquid separator 112 may also include a first temperature sensor 1128. The first temperature sensor 1128 may be installed on the connecting pipe 1127. The first temperature sensor 1128 monitors the temperature in real time and controls the heating to start and stop. For example, the heating is turned off when the temperature is 50°C and turned on when the temperature is 20°C to prevent the compressor oil from carbonizing due to excessive heating temperature.

[0145] Understandably, the first heat storage material 1126 encapsulates the heating element 1124 and the first heat exchange coil 1125, providing excellent insulation and heat preservation. When the heating element 1124 heats up, the first heat storage material 1126 can quickly absorb and store heat, reducing heat loss to the external environment. Simultaneously, after the heating element 1124 stops heating, the first heat storage material 1126 can slowly release the stored heat, continuing to provide heat to the refrigerant in the first heat exchange coil 1125 and the gas distribution coil 1123, maintaining system temperature stability and further reducing heat loss. Furthermore, the double-layer structure of the first shell 1121 and the second shell 1122 increases the heat transfer path and resistance, reducing heat conduction loss and improving the overall system's energy utilization efficiency.

[0146] The thermal management system 10 provided in this application embodiment achieves staged heating control through the above-described structure design of the heated gas-liquid separator 112. The first heat exchange coil 1125 preheats the refrigerant to near saturation temperature, and the gas separation coil 1123 further heats it to completely vaporize it, maximizing the heating efficiency. At the same time, the first heat storage material 1126 forms a heat insulation buffer layer, so that the heat generated by the heating part 1124 is only transferred to the first heat exchange coil 1125 and the gas separation coil 1123, thereby significantly reducing heat loss. Furthermore, the heat that is not absorbed in time can be stored in the heat storage material and continuously released when the heating part 1124 stops working, reducing the start-stop frequency of the heating part 1124 and thus reducing energy consumption per unit time.

[0147] In some embodiments, such as Figure 6 , Figure 13 , Figure 28 and Figure 29 As shown, the thermal management system 10 also includes a heating device 17.

[0148] The heating device 17 is connected in parallel to the first heat exchanger 12a2.

[0149] The heating device 17 is a separate component that generates heat to provide additional thermal energy to the thermal management system 10.

[0150] In this embodiment, such as Figure 6 , Figure 13 , Figure 28 and Figure 29 As shown, a first solenoid valve 181 and a second solenoid valve 182 can be installed at the inlet and outlet ends of the first heat exchanger 12a2. The first solenoid valve 181 and the second solenoid valve 182 can be used to regulate the amount of refrigerant flowing through the first heat exchanger 12a2. A third solenoid valve 183 can be installed on the parallel branch where the heating device 17 is located. The third solenoid valve 183 can be used to regulate the amount of refrigerant flowing through the heating device 17.

[0151] In actual operation, under extremely cold conditions, the refrigerant temperature is low, resulting in insufficient suction superheat upon entering the compressor 111, which may lead to difficulty in starting the compressor 111 or unstable operation. However, the independently installed heating device 17, connected in parallel to the first heat exchanger 12a2, can directly heat the incoming refrigerant before the heating mode is activated, increasing its temperature and enthalpy, and thus increasing the suction superheat of the compressor 111. This allows the compressor 111 to reach normal operating conditions in a shorter time, quickly starting the heating mode to heat the energy storage battery, and improving the adaptability and start-up performance of the thermal management system 10 in extremely cold environments.

[0152] In addition, the thermal management system 10 can also be configured with a defrost mode. In the defrost mode, the independent heating device 17 starts to work. The heating device 17 is connected in parallel with the first heat exchanger 12a2, providing an additional heating source for the high-pressure side refrigerant. The heat generated by the heating device 17 raises the temperature of part of the refrigerant. After this part of the high-temperature refrigerant mixes with the refrigerant flowing out of the first heat exchanger 12a2, the overall temperature and enthalpy of the refrigerant increase. The high-temperature, high-enthalpy refrigerant can transfer heat to the frost layer more quickly, causing the frost layer to melt rapidly, thereby accelerating the defrost speed, reducing the defrost time, and improving the operating efficiency and stability of the thermal management system 10.

[0153] The thermal management system 10 provided in this application embodiment, through the setting of the heating device 17, on the one hand, can directly increase the refrigerant temperature, so that the superheat of the compressor 111 suction can quickly reach a safe value, realizing rapid start-up heating in extremely cold environments and improving the environmental adaptability of the system. On the other hand, when the defrosting effect is difficult to achieve as expected, the heating device 17 can provide additional heat, increase the temperature and enthalpy of the high-pressure side refrigerant, accelerate the defrosting process, and thus significantly shorten the defrosting time. Furthermore, the independent heating device 17 is easy to maintain, and the failure does not affect the operation of the main system.

[0154] In some embodiments, such as Figure 28 and Figure 29 As shown, the heating device 17 includes: a housing 171, a heating element 172, and a second heat exchange coil 173.

[0155] The housing 171 is provided with a second heat storage material 174; the heating element 172 and the second heat exchange coil 173 are separated and arranged in the housing 171, and the heating element 172 and the second heat exchange coil 173 are both wrapped by the second heat storage material 174.

[0156] The housing 171 serves as the external protection and containment structure for the heating device 17, providing a stable and enclosed space for the internal components, preventing external environmental factors from damaging the internal components, and also playing a certain role in safety protection.

[0157] The heating element 172 is the core heating component of the heating device 17. It generates heat through the conversion of electrical energy or other energy sources to provide a heat source for the entire heating device 17.

[0158] The heating element 172 can be an electric heating tube, a PTC (Positive Temperature Coefficient) heating element, or a thin film heating plate, etc., and this application embodiment does not limit this.

[0159] The second heat exchange coil 173 is a component used to realize heat transfer. The second heat exchange coil 173 exchanges heat with the heating element 172 through the second heat storage material 174, and transfers heat to the refrigerant flowing inside, thereby outputting heat to the thermal management system 10.

[0160] The second heat storage material 174 can be a liquid or a solid powder, and this application embodiment does not limit it.

[0161] Specifically, the second heat storage material 174 may include, but is not limited to, paraffin-based phase change materials, inorganic hydrated salt phase change materials, aluminum powder or magnesium oxide powder, etc., and the embodiments of this application do not limit this.

[0162] In this embodiment, such as Figure 28 and Figure 29 As shown, when the heating element 172 is working, the second heat storage material 174 absorbs and stores a large amount of heat. During rapid heating in extremely cold environments, even if the heating element 172 needs to reduce its power or stop working after reaching a high temperature in a short time to prevent overheating, the heat stored in the second heat storage material 174 can continue to be released, providing a stable heat source for the second heat exchange coil 173. This allows the first heat exchanger 12a2 to continuously obtain heat, thus enabling the thermal management system 10 to start heating quickly and stably, solving the problem of unstable heating caused by power fluctuations in the heating element 172. During defrosting, the heating element 172 may not need to work continuously or may continue to work at high power. The heat stored in the second heat storage material 174 can continue to heat the second heat exchange coil 173 when the heating element 172 reduces its power or stops working, extending the heating time, allowing the frost layer to melt fully, improving the defrosting effect, reducing the number of defrosting operations, and minimizing the impact on system performance.

[0163] It should be noted that, as Figure 28 and Figure 29 As shown, the heating device 17 may also include a second temperature sensor 175. The second temperature sensor 175 may be set at the outlet end of the second heat exchange coil 173. The heating is turned on and off in real time by monitoring the temperature through the second temperature sensor 175. For example, heating is turned off when the temperature is 50°C and turned on when the temperature is 20°C, so as to prevent the compressor oil from carbonizing due to excessive heating temperature.

[0164] Understandably, the heating element 172 and the second heat exchange coil 173 are separated and encased by the second heat storage material 174, allowing the heat generated by the heating element 172 to be evenly transferred to the second heat storage material 174, and then evenly transferred by the second heat storage material 174 to the second heat exchange coil 173. This structure solves the problem of uneven heating of the second heat exchange coil 173 caused by local overheating of the heating element 172, improving the efficiency and uniformity of heat transfer, thereby enhancing the overall performance stability of the thermal management system 10. Furthermore, the uniform heat transfer makes the temperature distribution on the surface of the second heat exchange coil 173 more uniform, resulting in more thorough heat exchange between the second heat exchange coil 173 and the refrigerant, improving heat exchange efficiency, reducing energy loss, and further enhancing the energy utilization efficiency of the thermal management system 10.

[0165] The thermal management system 10 provided in this application embodiment, through the structural design of the heating device 17, enables the second heat storage material 174 to evenly distribute heat to the second heat exchange coil 173 through thermal conduction. When the refrigerant flows through the second heat exchange coil 173, it is heated stably, reducing local overheating. At the same time, the second heat storage material 174 forms a heat insulation buffer layer, so that the heat generated by the heating element 172 is only transferred to the second heat exchange coil 173, thereby significantly reducing heat loss. Furthermore, the heat that is not absorbed immediately can be stored in the heat storage material and continuously released when the heating device 17 stops working, reducing the start-stop frequency of the heating device 17, thereby reducing energy consumption per unit time.

[0166] The embodiments of this application will be described in detail below from four different implementation perspectives.

[0167] I. For example Figures 1-5 As shown, the thermal management system 10 adopts a gas-liquid separator 112 with an integrated heating unit 1124, and the first heat exchanger 12a2 is subjected to forced air cooling heat exchange through the second fan 152 and the second air duct 162, and the precooler 141 is subjected to forced air cooling heat exchange through the third fan 153 and the third air duct 163.

[0168] In actual operation, the thermal management system 10 is configured with cooling mode, heating mode, self-circulation mode, and defrosting mode, such as... Figure 2As shown, when the thermal management system 10 switches to cooling mode, in cooling mode, the first refrigerant main line 11 and the second refrigerant main line 12a are connected end-to-end, and the first refrigerant main line 11, the first heat exchanger 12a2, and the bypass branch line 12b are sequentially connected end-to-end. The second heat exchanger 12a3 is used to cool the energy storage battery. For example, when the external ambient temperature is greater than or equal to 30°C, the overall subcooling of the thermal management system 10 can be controlled to 10°C to 15°C, which ensures sufficient exhaust superheat of the compressor 111 and facilitates refrigerant distribution. When the external ambient temperature is less than 30°C, the compressor 111 operates at a low frequency and the refrigerant flow rate is low; the overall subcooling of the thermal management system 10 can be set to 5°C to prevent increased flow resistance due to excessive liquid refrigerant.

[0169] Among them, such as Figure 2 As shown, primary subcooling = saturation temperature corresponding to P1 - T7; secondary subcooling = T8 - T9; overall subcooling = saturation temperature corresponding to P1 - T9. The second expansion valve 12b1 can control its opening according to the overall subcooling to ensure that the system maintains a suitable subcooling. Under low ambient temperature refrigeration conditions, when the system detects primary subcooling = 5℃, it controls the second expansion valve 12b1 to close, and secondary subcooling stops.

[0170] like Figure 3 As shown, when the thermal management system 10 switches to the heating mode, in the heating mode, the first refrigerant main line 11, the precooler 141 and the second refrigerant main line 12a are connected end to end in sequence, and the second heat exchanger 12a3 is used to heat up the energy storage battery.

[0171] For example, when the external ambient temperature is greater than or equal to -10°C, the first heat exchanger 12a2 acts as an evaporator for heat exchange, the heating unit 1124 does not operate, the compressor 111 can be set with different frequencies according to different external ambient temperature ranges, and the second fan 152 can be set with different speeds according to different external ambient temperature ranges. The control principle is to ensure that the condensing temperature does not exceed 40°C to prevent the battery cell temperature from becoming too high. The second expansion valve 12b1 is closed, and the opening degree of the first expansion valve 12a1 is controlled by the suction superheat. When the external ambient temperature is less than -10°C, the heating unit 1124 of the gas-liquid separator 112 acts as an evaporator for heat exchange, the second fan 152 does not operate, the compressor 111 can be set with different frequencies according to different external ambient temperature ranges, the control principle is to ensure that the condensing temperature does not exceed 40°C to prevent the battery cell temperature from becoming too high, the second expansion valve 12b1 is closed, and the opening degree of the first expansion valve 12a1 is controlled by the suction superheat.

[0172] When the exhaust temperature is greater than or equal to 30℃ and the sensible heat superheat is greater than 1℃, the third fan 153 is turned on. After the third fan 153 matched with the precooler 141 is turned on, the fan speed is adjusted according to the sensible heat superheat. If there is more than one third fan 153, the speed of each third fan 153 is kept consistent. For example, Figure 3 As shown, the sensible superheat is equal to the saturation temperature corresponding to T4 - P4. By adjusting the speed of the third fan 153, the sensible superheat is ensured to be between 0℃ and 2℃. The speed adjustment cycle of the third fan 153 can be 30 seconds, and each adjustment can be set to 30 rpm.

[0173] Since the multiple secondary heat exchangers 12a3 in the energy storage system are usually arranged vertically, if heating is carried out for a long time, liquid can easily accumulate in the bottom secondary heat exchanger 12a3, resulting in poor temperature uniformity of the battery cells. In this case, if... Figure 4 As shown, the thermal management system 10 can be switched to a self-circulation mode. In the self-circulation mode, the compressor 111 operates at a self-circulation frequency. The first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence.

[0174] For example, during continuous operation in heating mode, when the thermal management system 10 detects a cell temperature difference greater than 8°C, the second fan 152, heating element 1124, and third fan 153 all stop and switch to self-circulation mode. The refrigerant flow direction in self-circulation mode is consistent with that in cooling mode. The second expansion valve 12b1 controls subcooling, and the first expansion valve 12a1 throttles and reduces pressure. If the cell temperature difference is less than 4°C, or if P1 rises to 40 bar or P2 rises to 40 bar, the system exits self-circulation mode and re-enters heating mode.

[0175] like Figure 5 As shown, when the thermal management system 10 switches to defrost mode, the second expansion valve 12b1 is fully open, the first expansion valve 12a1 is closed, and both the second fan 152 and the third fan 153 are stopped. The first refrigerant main line 11, the first heat exchanger 12a2, and the bypass branch line 12b are connected sequentially. The refrigerant does not pass through the second heat exchanger 12a3 to prevent the temperature of the energy storage battery from dropping due to excessively low temperature of the second heat exchanger 12a3 during defrost.

[0176] For example, after entering defrost mode for 3 minutes, the heating unit 1124 is activated every 2 minutes of defrost mode operation. The heating unit 1124 operates for 30 seconds or its temperature reaches 50°C, and then the heating unit 1124 is turned off. By operating the heating unit 1124, the suction temperature of the compressor 111 is increased, the liquid refrigerant content is reduced, the refrigerant circulation volume is increased, and the defrost efficiency is improved.

[0177] II. Figures 6-12As shown, the thermal management system 10 adopts an independent heating device 17, and the first heat exchanger 12a2 is subjected to forced air cooling heat exchange through the second fan 152 and the second air duct 162, and the precooler 141 is subjected to forced air cooling heat exchange through the third fan 153 and the third air duct 163.

[0178] In actual operation, the thermal management system 10 is configured with cooling mode, heating mode, self-circulation mode, and defrosting mode, such as... Figure 7 As shown, when the thermal management system 10 switches to the cooling mode, in the cooling mode, the first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence. The second heat exchanger 12a3 is used to cool the energy storage battery.

[0179] The control logic of the second thermal management system 10 in cooling mode can refer to the control logic of the first thermal management system 10 in cooling mode, which will not be repeated here.

[0180] When the thermal management system 10 switches to heating mode, in heating mode, if the external ambient temperature is greater than or equal to the set value, such as Figure 8 As shown, the first refrigerant main line 11, the precooler 141, and the second refrigerant main line 12a are connected sequentially. The first solenoid valve 181 and the second solenoid valve 182 are open, and the third solenoid valve 183 is closed. The first heat exchanger 12a2 is used as an evaporator, and the second heat exchanger 12a3 is used to heat the energy storage battery. When the external ambient temperature is lower than the set value, such as Figure 9 As shown, the first refrigerant main line 11, precooler 141, second heat exchanger 12a3, liquid receiver 12a5, first line 124a of subcooler 124, second line 143b of regenerator 143, dryer filter 12a4 and heating device 17 are connected in sequence. The first solenoid valve 181 and the second solenoid valve 182 are closed, and the third solenoid valve 183 is open. The heating device 17 is used as an evaporator, and the second heat exchanger 12a3 is used to heat the energy storage battery.

[0181] The control logic of the second thermal management system 10 in heating mode can refer to the control logic of the first thermal management system 10 in heating mode, which will not be repeated here.

[0182] like Figure 10 As shown, the thermal management system 10 can be switched to a self-circulation mode. In the self-circulation mode, the compressor 111 operates at a self-circulation frequency. The refrigerant flow direction in the self-circulation mode is the same as that in the refrigeration mode. That is, the first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence.

[0183] The control logic of the third thermal management system 10 in self-circulation mode can refer to the control logic of the first thermal management system 10 in self-circulation mode mentioned above, and will not be repeated here.

[0184] When the thermal management system 10 switches to defrost mode, in defrost mode, the second expansion valve 12b1 is fully open, the first expansion valve 12a1 is closed, and both the second fan 152 and the third fan 153 are stopped. Figure 11 As shown, the first refrigerant main line 11, the first heat exchanger 12a2, and the bypass branch line 12b are connected sequentially. The refrigerant does not pass through the second heat exchanger 12a3 to prevent the temperature of the energy storage battery from dropping due to excessively low temperature of the second heat exchanger 12a3 during defrosting. To further optimize the defrosting effect, such as... Figure 12 As shown, based on the above refrigerant flow direction, the third solenoid valve 183 is further opened to start the heating device 17.

[0185] The control logic of the second thermal management system 10 in defrost mode can refer to the control logic of the first thermal management system 10 in defrost mode, which will not be repeated here.

[0186] III. Figures 13-18 As shown, the thermal management system 10 adopts an independent heating device 17, and the first heat exchanger 12a2 and the precooler 141 share the first fan 151 and the first air duct 161 for forced air cooling heat exchange.

[0187] In actual operation, the thermal management system 10 is configured with cooling mode, heating mode, self-circulation mode, and defrosting mode, such as... Figure 14 As shown, when the thermal management system 10 switches to the cooling mode, in the cooling mode, the first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence. The second heat exchanger 12a3 is used to cool the energy storage battery.

[0188] The control logic of the third thermal management system 10 in cooling mode can refer to the control logic of the first thermal management system 10 in cooling mode, and will not be repeated here.

[0189] When the thermal management system 10 switches to heating mode, in heating mode, such as Figure 15 As shown, the first refrigerant main line 11, precooler 141, second heat exchanger 12a3, liquid receiver 12a5, first line 124a of subcooler 124, second line 143b of regenerator 143, dryer filter 12a4 and heating device 17 are connected in sequence. The first solenoid valve 181 and the second solenoid valve 182 are closed, and the third solenoid valve 183 is open. The heating device 17 is used as an evaporator, and the second heat exchanger 12a3 is used to heat the energy storage battery.

[0190] like Figure 16 As shown, the thermal management system 10 can be switched to a self-circulation mode. In the self-circulation mode, the compressor 111 operates at a self-circulation frequency. The refrigerant flow direction in the self-circulation mode is the same as that in the refrigeration mode. That is, the first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence.

[0191] The control logic of the third thermal management system 10 in self-circulation mode can refer to the control logic of the first thermal management system 10 in self-circulation mode mentioned above, and will not be repeated here.

[0192] When the heat management system 10 switches to defrost mode, in defrost mode, the second expansion valve 12b1 is fully open, the first expansion valve 12a1 is closed, and the first fan 151 stops. Figure 17 As shown, the first refrigerant main line 11, the first heat exchanger 12a2, and the bypass branch line 12b are connected sequentially. The refrigerant does not pass through the second heat exchanger 12a3 to prevent the temperature of the energy storage battery from dropping due to excessively low temperature of the second heat exchanger 12a3 during defrosting. To further optimize the defrosting effect, such as... Figure 18 As shown, based on the above refrigerant flow direction, the third solenoid valve 183 is further opened to start the heating device 17.

[0193] The control logic of the third thermal management system 10 in defrost mode can refer to the control logic of the first thermal management system 10 in defrost mode, which will not be repeated here.

[0194] IV. Figures 19-23 As shown, the thermal management system 10 adopts a gas-liquid separator 112 with an integrated heating unit 1124, and the first heat exchanger 12a2 and the precooler 141 share the first fan 151 and the first air duct 161 for forced air cooling heat exchange.

[0195] In actual operation, the thermal management system 10 is configured with cooling mode, heating mode, self-circulation mode, and defrosting mode, such as... Figure 20 As shown, when the thermal management system 10 switches to the cooling mode, in the cooling mode, the first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence. The second heat exchanger 12a3 is used to cool the energy storage battery.

[0196] The control logic of the fourth thermal management system 10 in cooling mode can refer to the control logic of the first thermal management system 10 in cooling mode, and will not be repeated here.

[0197] like Figure 21As shown, when the thermal management system 10 switches to heating mode, in heating mode, the first refrigerant main line 11, the precooler 141, and the second refrigerant main line 12a are connected end to end in sequence, and the second heat exchanger 12a3 is used to heat the energy storage battery. The gas-liquid separator 112 starts the heating section 1124. Since the first fan 151 has a low speed, the heat exchange of the first heat exchanger 12a2 is extremely small and negligible. The low-pressure side mainly exchanges heat through the heating section 1124, that is, the heating section 1124 is used as an evaporator.

[0198] like Figure 22 As shown, when the thermal management system 10 switches to the self-circulation mode, the compressor 111 operates at the self-circulation frequency in the self-circulation mode. The first refrigerant main line 11 and the second refrigerant main line 12a are connected end to end, and the first refrigerant main line 11, the first heat exchanger 12a2 and the bypass branch line 12b are connected end to end in sequence.

[0199] The control logic of the fourth thermal management system 10 in self-circulation mode can refer to the control logic of the first thermal management system 10 in self-circulation mode mentioned above, and will not be repeated here.

[0200] like Figure 23 As shown, when the thermal management system 10 switches to defrost mode, the second expansion valve 12b1 is fully open, the first expansion valve 12a1 is closed, the first fan 151 stops, and the first refrigerant main line 11, the first heat exchanger 12a2, and the bypass branch line 12b are connected sequentially. The refrigerant does not pass through the second heat exchanger 12a3 to prevent the temperature of the energy storage battery from dropping due to excessively low temperature of the second heat exchanger 12a3 during defrost.

[0201] The control logic of the fourth thermal management system 10 in defrost mode can refer to the control logic of the first thermal management system 10 in defrost mode, and will not be repeated here.

[0202] This application also discloses an energy storage system.

[0203] In some embodiments, the energy storage system includes: an energy storage battery and a thermal management system 10 as described in any of the above embodiments.

[0204] The thermal management system 10 is electrically connected to the energy storage battery.

[0205] The energy storage system provided in this application embodiment, through the setting of the aforementioned thermal management system 10, utilizes the second expansion valve 12b1 to throttle and cool a portion of the refrigerant, allowing it to enter the second path 124b of the subcooler 124 for secondary subcooling of the refrigerant in the first path 124a of the subcooler 124. This effectively increases the subcooling degree of the refrigerant, resulting in a higher liquid proportion in the refrigerant entering the second heat exchanger 12a3 after throttling by the first expansion valve 12a1. This provides more usable liquid refrigerant for the evaporation process, thereby extending the duration of the gas-liquid two-phase state of the refrigerant in the second heat exchanger 12a3. This effectively alleviates the premature complete evaporation of the refrigerant, ensuring that there is still sufficient liquid refrigerant at the outlet of the second heat exchanger 12a3 for evaporation and heat absorption. This significantly improves the temperature uniformity of the energy storage battery, alleviates the situation where the cell temperature is higher closer to the outlet of the second heat exchanger 12a3, and thus extends the service life of the energy storage battery, improving the reliability and stability of the energy storage system.

[0206] This application also discloses a photovoltaic energy storage system.

[0207] In some embodiments, the photovoltaic energy storage system includes a photovoltaic power generation system and an energy storage system as described above.

[0208] Photovoltaic power generation systems are used to power energy storage systems.

[0209] The photovoltaic energy storage system provided in this application embodiment, through the configuration of the energy storage system, utilizes the second expansion valve 12b1 to throttle and cool a portion of the refrigerant, allowing it to enter the second path 124b of the subcooler 124 for secondary subcooling of the refrigerant in the first path 124a of the subcooler 124. This effectively increases the subcooling degree of the refrigerant, resulting in a higher liquid proportion in the refrigerant entering the second heat exchanger 12a3 after throttling by the first expansion valve 12a1. This provides more usable liquid refrigerant for the evaporation process, thereby extending the duration of the gas-liquid two-phase state of the refrigerant in the second heat exchanger 12a3. This effectively alleviates the premature complete evaporation of the refrigerant, ensuring that there is still sufficient liquid refrigerant at the outlet of the second heat exchanger 12a3 for evaporation and heat absorption. This significantly improves the temperature uniformity of the energy storage battery, alleviates the situation where the cell temperature is higher closer to the outlet of the second heat exchanger 12a3, and thus extends the service life of the energy storage battery, improving the reliability and stability of the energy storage system.

[0210] The terms "first," "second," etc., used in the specification and claims of this application are used to distinguish similar objects and not to describe a specific order or sequence. It should be understood that such use of data can be interchanged where appropriate so that embodiments of this application can be implemented in orders other than those illustrated or described herein, and the objects distinguished by "first," "second," etc., are generally of the same class and the number of objects is not limited; for example, a first object can be one or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0211] In the description of this application, it should be understood that the terms "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0212] In the description of this application, "first feature" and "second feature" may include one or more of the features.

[0213] In the description of this application, "multiple" means two or more.

[0214] In the description of this application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or the first and second features being in contact through another feature between them.

[0215] In the description of this application, the terms "above," "over," and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0216] Other configurations of the embodiments of this application, such as ... and ..., and operations, are known to those skilled in the art and will not be described in detail here.

[0217] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0218] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A thermal management system (10) applied to an energy storage system, characterized in that, include: The first refrigerant main circuit (11) includes a compressor (111) and a gas-liquid separator (112); The second refrigerant main line (12a) is adapted to be connected to the first refrigerant main line (11) and includes a first heat exchanger (12a2), a first line of a subcooler (124), a first expansion valve (12a1), and a second heat exchanger (12a3) connected in sequence. The second heat exchanger (12a3) is used to exchange heat with the energy storage battery of the energy storage system. The bypass branch (12b) includes a second expansion valve (12b1) and a second path of the subcooler (124). The inlet of the bypass branch (12b) is connected between the first heat exchanger (12a2) and the first path of the subcooler (124), and the outlet of the bypass branch (12b) is connected between the second heat exchanger (12a3) and the gas-liquid separator (112).

2. The thermal management system (10) according to claim 1, characterized in that, Also includes: A four-way valve (13) includes a first to a fourth valve port (134), the first valve port (131) being connected to the compressor (111), the second valve port (132) being connected to the gas-liquid separator (112), the third valve port (133) being connected to the first heat exchanger (12a2), and the fourth valve port (134) being connected to the second heat exchanger (12a3).

3. The thermal management system (10) according to claim 2, characterized in that, Also includes: A precooler (141) is provided, the inlet of which is connected to the fourth valve port (134), and the outlet of which is connected to the second heat exchanger (12a3).

4. The thermal management system (10) according to claim 3, characterized in that, Also includes: The first fan (151) and the thermal management system (10) form a first air duct (161). The first fan (151) is used to drive the airflow in the first air duct (161). The first air duct (161) is connected to the gas flow channel of the first heat exchanger (12a2) and the gas flow channel of the precooler (141).

5. The thermal management system (10) according to claim 3, characterized in that, Also includes: The second fan (152) forms a second air duct (162) in the thermal management system (10). The second fan (152) is used to drive the airflow in the second air duct (162). The second air duct (162) is connected to the gas flow channel of the first heat exchanger (12a2). The third fan (153) forms a third air duct (163) in the thermal management system (10). The third fan (153) is used to drive the airflow in the third air duct (163). The third air duct (163) is connected to the gas flow channel of the precooler (141) and is separated from the gas flow channels of the second air duct (162) and the first heat exchanger (12a2).

6. The thermal management system (10) according to claim 2, characterized in that, Also includes: The regenerator (143) has its first inlet connected to the second heat exchanger (12a3), its first outlet connected to the fourth valve port (134), its second outlet connected between the first heat exchanger (12a2) and the subcooler (124), and the inlet of the bypass branch (12b) connected between the first heat exchanger (12a2) and the first outlet of the subcooler (124), and the outlet of the bypass branch (12b) connected between the outlet of the regenerator (143) and the fourth valve port (134).

7. The thermal management system (10) according to any one of claims 1-6, characterized in that, The gas-liquid separator (112) has a heating section (1124).

8. The thermal management system (10) according to claim 7, characterized in that, The gas-liquid separator (112) includes: First shell (1121); The second shell (1122) is disposed inside the first shell (1121), and a first heat storage material (1126) is disposed between the first shell (1121) and the second shell (1122); Gas distribution coil (1123) is connected to the second housing (1122); The first heat exchange coil (1125) and the heating part (1124) are both located between the first shell (1121) and the second shell (1122), and are both wrapped by the first heat storage material (1126). The outlet of the first heat exchange coil (1125) is connected to the inlet of the gas distribution coil (1123).

9. The thermal management system (10) according to any one of claims 1-6, further comprising: Heating device (17) is connected in parallel to the first heat exchanger (12a2).

10. The thermal management system (10) according to claim 9, characterized in that, The heating device (17) includes: The shell (171) is provided with a second heat storage material (174) inside; The heating element (172) and the second heat exchange coil (173) are separately disposed in the housing (171) and are both wrapped by the second heat storage material (174).

11. An energy storage system, characterized in that, include: Energy storage batteries; The thermal management system (10) according to any one of claims 1-10, wherein the thermal management system (10) is electrically connected to the energy storage battery.

12. A photovoltaic energy storage system, characterized in that, include: The energy storage system of claim 11; A photovoltaic power generation system, wherein the photovoltaic power generation system is used to supply power to the energy storage system.

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