Temperature control system

Abstract

The embodiment of the application provides a temperature control system, comprising a refrigerant circulation subsystem and a cooling liquid circulation subsystem; the refrigerant circulation subsystem comprises a battery liquid cooling assembly, a driving device, a compressor driving module and a driving liquid cooling plate; the refrigerant circulation subsystem comprises a compressor, a first heat exchanger, a first four-way valve, a second four-way valve, a first expansion valve, a second expansion valve and a three-way valve; the temperature control system further comprises a second heat exchanger, refrigerant flowing out from a first interface flows through the second heat exchanger to a third port in sequence, and the second heat exchanger exchanges heat with cooling liquid flowing out from an outlet end of the driving device; a third heat exchanger, refrigerant flowing out from an outlet end of the compressor flows through the second expansion valve, a first port, a third port and the third heat exchanger to an inlet end of the first heat exchanger, and the third heat exchanger exchanges heat with the cooling liquid flowing out from the outlet end of the driving device. The temperature control system of the application can effectively dissipate heat for the compressor driving module.

Description

Technical Field

[0001] This application relates to the field of temperature control technology, specifically to a temperature control system. Background Technology

[0002] As the energy storage industry develops on a large scale, the demand for heat dissipation from energy storage batteries continues to increase, leading to a corresponding increase in the cooling capacity requirement for temperature control units. To match the higher cooling capacity output, the temperature control system needs to be equipped with compressors that have higher power consumption and larger displacement. As the core control component, the heat load generated by the compressor drive module increases significantly with the increase in compressor power.

[0003] To address the heat dissipation requirements of the compressor drive module, traditional energy storage temperature control systems generally employ air cooling. This method uses a fan to force airflow away heat from the surface of the compressor drive module, maintaining its temperature within a certain range.

[0004] However, with the increase in compressor power and the increase in the heat load of compressor drive modules, the drawbacks of traditional air-cooling heat dissipation methods have become increasingly apparent. Their heat dissipation capacity has a clear upper limit and is difficult to meet the heat dissipation requirements of current high-power compressor drive modules. Summary of the Invention

[0005] The purpose of this invention is to solve the above-mentioned problems and other issues.

[0006] Another objective of this invention is to provide a temperature control system capable of effectively dissipating heat from the compressor drive module.

[0007] The purpose of this invention is not limited to the purposes mentioned above, and those skilled in the art will clearly understand other purposes not mentioned from the following description.

[0008] In some embodiments of this application, a temperature control system is provided, including a refrigerant circulation subsystem and a coolant circulation subsystem; the coolant circulation subsystem includes: Battery liquid cooling components are used to exchange heat between the coolant flowing through them and the energy storage battery. A drive unit for driving the coolant; The compressor drive module is connected to the compressor; A liquid cooling plate is installed to fit the compressor drive module. The refrigerant cycle subsystem includes: A compressor is used to compress refrigerant; A first heat exchanger is used to exchange heat between the refrigerant flowing through it and the air. The first four-way valve has a first port, a second port, a third port and a fourth port, wherein the third port is connected to the inlet end of the first heat exchanger and the fourth port is connected to the outlet end of the compressor. The second four-way valve has a first port, a second port, a third port and a fourth port, the first port being connected to the outlet end of the first heat exchanger and the second port being connected to the inlet end of the compressor; The first expansion valve is connected at both ends to the second interface and the fourth port, respectively. The second expansion valve is connected at one end to the outlet end of the compressor; The three-way valve has a first port, a second port and a third port, the first port being connected to the other end of the second expansion valve, and the second port being connected to the inlet end of the first heat exchanger; The temperature control system also includes: The refrigerant flowing out of the first port flows through the second heat exchanger to the third port, where it exchanges heat with the coolant flowing out of the outlet of the drive device. The refrigerant flowing from the outlet of the compressor flows through the second expansion valve, the first port, the third port, and the third heat exchanger to the inlet of the first heat exchanger, where it exchanges heat with the coolant flowing from the outlet of the drive device.

[0009] The above technical solution has the following advantages or beneficial effects: the coolant circulation subsystem includes a drive liquid cooling plate, which is set in conjunction with the compressor drive module. The coolant flowing through the drive liquid cooling plate exchanges heat with the compressor drive module. Compared with air cooling, liquid cooling through coolant has stronger heat dissipation capacity and higher heat dissipation efficiency, solving the technical problems of insufficient heat dissipation capacity and weak heat dissipation efficiency of traditional air cooling.

[0010] The temperature control system is divided into a refrigerant circulation subsystem and a coolant circulation subsystem, separating the refrigerant circulation loop from the coolant circulation loop. Heat exchange is achieved only through a heat exchanger, without direct medium mixing or loop interconnection, ensuring the operational stability of the temperature control system. Furthermore, heat exchange is conducted between the coolant and the compressor drive module. Since the coolant is a single-phase fluid with no phase change process, its temperature change is gradual, further ensuring the operational stability of the temperature control system. This solves the technical problem of system instability caused by using refrigerant to dissipate heat from the compressor drive module.

[0011] After the refrigerant is compressed by the compressor, a high-temperature refrigerant is obtained. This high-temperature refrigerant flows sequentially through the second expansion valve, the first port, the third port, and the third heat exchanger. In the third heat exchanger, it exchanges heat with the coolant flowing out of the drive unit's outlet. By utilizing the waste heat from the compressor exhaust, the surface temperature of the drive liquid cooling plate can be increased with lower energy consumption compared to electric heating, thus preventing condensation on the drive liquid cooling plate. The high-temperature refrigerant, obtained by the compressor compression, flows sequentially through the second expansion valve, the first port, the second port, and finally to the first heat exchanger. Utilizing the waste heat from the compressor exhaust solves the high energy consumption problem caused by electric heating.

[0012] In some embodiments of this application, a temperature control system is provided, the temperature control system further comprising: Control unit, the control unit is configured to: When the temperature control system operates in cooling mode, the second port is closed, and the refrigerant flowing from the compressor outlet flows sequentially through the fourth port, the third port, the first heat exchanger, the first port, the fourth port, the first expansion valve, the second port, the first port, the second heat exchanger, the third port, and the second port to the compressor inlet, forming the first refrigerant main circuit; and The refrigerant flowing out from the outlet of the compressor flows sequentially through the second expansion valve, the first port, the third port, the third heat exchanger, and the first heat exchanger to form a first refrigerant waste heat utilization branch.

[0013] In some embodiments of this application, a temperature control system is provided, wherein the compressor drive module is located inside an electrical control box, and the coolant circulation subsystem further includes: A flow regulating valve is used to regulate the flow rate of the coolant flowing through it; A temperature sensor for driving the liquid cooling plate is used to detect the surface temperature of the driving liquid cooling plate. A compressor drive module temperature sensor is used to detect the operating temperature of the compressor drive module; The control unit is also configured to: When the temperature control system is operating in cooling mode, it controls the flow regulating valve to be fully open and the second expansion valve to be fully closed. If the surface temperature of the driving liquid cooling plate is detected to be below the set temperature of the driving liquid cooling plate, the second expansion valve is adjusted to make the surface temperature of the driving liquid cooling plate reach the set temperature of the driving liquid cooling plate, wherein the set temperature of the driving liquid cooling plate is determined based on the dew point temperature inside the electrical control box and is greater than the dew point temperature inside the electrical control box.

[0014] The above technical solution has the following advantages or beneficial effects: When the temperature control system is running in cooling mode, the flow regulating valve is fully open to maximize the flow of coolant through the driving liquid cooling plate, thereby maximizing the removal of the dynamic heat load of the compressor drive module and preventing heat accumulation due to insufficient coolant flow. The second expansion valve is also fully closed to cut off the refrigerant flow in the first refrigerant waste heat utilization branch, preventing refrigerant diversion in the first refrigerant main circuit and ensuring that the cooling efficiency of the first refrigerant main circuit is not disturbed. If the surface temperature of the driving liquid cooling plate is detected to be below the set temperature (which is determined based on the dew point temperature inside the control box and is higher than the dew point temperature inside the control box), indicating that condensation is about to occur in the coolant, the second expansion valve is adjusted to bring the surface temperature of the driving liquid cooling plate up to the set temperature. This replenishes the temperature of the driving liquid cooling plate, preventing coolant condensation. Thus, a balance between condensation prevention and heat dissipation efficiency is effectively achieved, and hazards such as insulation degradation and short circuits to the electrical control system are avoided.

[0015] In some embodiments of this application, a temperature control system is provided, wherein the control unit is further configured to: If the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, the surface temperature of the drive liquid cooling plate is maintained at the set temperature of the drive liquid cooling plate, and the opening of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve; wherein, the set temperature of the compressor drive module is determined based on the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module; When the operating temperature of the compressor drive module is detected to reach the set temperature of the compressor drive module or the second expansion valve is fully closed, the adjustment of the flow regulating valve and the second expansion valve is stopped.

[0016] The above technical solution has the following advantages or beneficial effects: If the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, wherein the set temperature of the compressor drive module is determined based on the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module, it indicates that the heat load of the compressor drive module is lower than the current heat dissipation capacity and the temperature safety redundancy is sufficient. Then, the surface temperature of the drive liquid cooling plate is maintained at the set temperature of the drive liquid cooling plate, and the opening of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve. When the operating temperature of the compressor drive module is detected to reach the set temperature of the compressor drive module or the second expansion valve is fully closed, the adjustment of the flow regulating valve and the second expansion valve is stopped. Thus, based on preventing condensation and ensuring heat dissipation, the energy waste problem caused by the fixed control mode is solved through refined control.

[0017] In some embodiments of this application, a temperature control system is provided, wherein the control unit is further configured to: If the surface temperature of the driving liquid cooling plate is detected to be above the set temperature of the driving liquid cooling plate, the opening of the flow regulating valve and the second expansion valve shall be maintained. If the operating temperature of the compressor drive module is detected to be above the set temperature of the compressor drive module, the opening of the flow regulating valve and the second expansion valve shall be maintained.

[0018] The above technical solution has the following advantages or beneficial effects: If the surface temperature of the driving liquid cooling plate is detected to be above the set temperature of the driving liquid cooling plate, it indicates that the coolant will not condense. Therefore, the opening of the flow regulating valve and the second expansion valve are maintained to avoid frequent parameter fluctuations and improve the operational stability of the temperature control system. If the operating temperature of the compressor drive module is detected to be above the set temperature of the compressor drive module, it indicates that the heat load of the compressor drive module has approached its current heat dissipation capacity. Therefore, the opening of the flow regulating valve and the second expansion valve are maintained to avoid frequent parameter fluctuations and improve the operational stability of the temperature control system.

[0019] In some embodiments of this application, a temperature control system is provided, the temperature control system further comprising: Control unit, the control unit is configured to: When the temperature control system operates in heating mode, the third port is closed, and the refrigerant flowing from the compressor outlet flows sequentially through the fourth port, the first port, the second heat exchanger, the third port, the fourth port, the first expansion valve, the second port, the third port, the first heat exchanger, the first port, and the second port to the compressor inlet, thus forming a second refrigerant main circuit; and The refrigerant flowing out from the outlet of the compressor flows sequentially through the second expansion valve, the first port, the second port and the first heat exchanger to form a second refrigerant waste heat utilization branch.

[0020] In some embodiments of this application, a temperature control system is provided, wherein the compressor drive module is located inside an electrical control box, and the coolant circulation subsystem further includes: A flow regulating valve is used to regulate the flow rate of the coolant flowing through it; The control unit is also configured to: When the temperature control system is running in heating mode, it controls the flow regulating valve to be fully open and controls the opening of the second expansion valve to be in a half-open and half-closed state to defrost the outer surface of the first heat exchanger.

[0021] The above technical solution has the following advantages or beneficial effects: When the temperature control system is running in heating mode, the flow regulating valve is fully opened, allowing the coolant to flow through the drive liquid cooling plate at maximum flow rate, quickly removing heat and preventing the drive module temperature from exceeding the maximum allowable limit, thus ensuring stable compressor operation; and the opening degree of the second expansion valve is controlled to be in a half-open and half-closed state, accurately distributing the hot gas flow rate of the compressor exhaust, realizing non-stop defrosting of the outer surface of the first heat exchanger, ensuring the flow efficiency of the refrigerant and the heat exchange efficiency of the first heat exchanger.

[0022] In some embodiments of this application, a temperature control system is provided, wherein the refrigerant circulation subsystem further includes: Compressor suction temperature sensor, used to detect compressor suction temperature; Compressor suction pressure sensor, used to detect compressor suction pressure; The temperature control system further includes a control unit, which is configured to: The compressor evaporation temperature is determined based on the compressor suction pressure. Calculate the compressor suction superheat based on the compressor suction temperature and the compressor evaporation temperature; Calculate the difference in compressor suction superheat based on the compressor suction superheat and the target compressor suction superheat. Obtain the adjustment coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference; The opening degree of the first expansion valve is adjusted according to the adjustment coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference.

[0023] The above technical solution has the following advantages or beneficial effects: by adjusting the coefficient, the current compressor suction superheat difference and the historical compressor suction superheat difference, the opening of the first expansion valve can be precisely adjusted to avoid compressor failure caused by abnormal compressor suction superheat.

[0024] In some embodiments of this application, a temperature control system is provided, wherein the coolant circulation subsystem further includes: A liquid outlet temperature sensor is installed at the outlet end of the battery liquid cooling plate assembly to detect the liquid outlet temperature of the energy storage battery. The control unit is also configured to: If the temperature of the liquid outlet of the energy storage battery is detected to be above the first target temperature of the liquid outlet of the energy storage battery, the temperature control system is controlled to operate the cooling mode. If the outlet temperature of the energy storage battery is detected to be below the outlet temperature of the second target energy storage battery, the temperature control system is controlled to stop operating the cooling mode, whereby the outlet temperature of the second target energy storage battery is lower than the outlet temperature of the first target energy storage battery.

[0025] The above technical solution has the following advantages or beneficial effects: If the detected outlet temperature of the energy storage battery reaches or exceeds the first target outlet temperature, it indicates that the current temperature of the energy storage battery is too high, and the temperature control system is precisely controlled to operate in cooling mode. If the detected outlet temperature of the energy storage battery is below the second target outlet temperature, and the second target outlet temperature is lower than the first target outlet temperature, it indicates that the current temperature of the energy storage battery is not high, and the temperature control system is precisely controlled to stop operating in cooling mode.

[0026] In some embodiments of this application, a temperature control system is provided, wherein the coolant circulation subsystem further includes: A liquid outlet temperature sensor is located at the outlet end of the battery liquid cooling plate assembly and is used to detect the liquid outlet temperature of the energy storage battery. The control unit is also configured to: If the temperature of the liquid outlet of the energy storage battery is detected to be below the temperature of the third target energy storage battery, the temperature control system is controlled to operate the heating mode. If the detected temperature of the liquid outlet of the energy storage battery reaches or exceeds the second target temperature of the liquid outlet of the energy storage battery, the temperature control system is controlled to stop operating the heating mode, and the third target temperature of the liquid outlet of the energy storage battery is lower than the second target temperature of the liquid outlet of the energy storage battery.

[0027] The above technical solution has the following advantages or beneficial effects: If the detected outlet temperature of the energy storage battery is below the third target outlet temperature, it indicates that the current temperature of the energy storage battery is too low, and the temperature control system is precisely controlled to operate in heating mode. If the detected outlet temperature of the energy storage battery reaches above the second target outlet temperature, and the third target outlet temperature is lower than the second target outlet temperature, it indicates that the current temperature of the energy storage battery is not low, and the temperature control system is precisely controlled to stop operating in heating mode.

[0028] The effects of the above-mentioned technical solutions are not limited to those mentioned above. Those skilled in the art can clearly understand other effects not mentioned from the description in the claims. Attached Figure Description

[0029] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. It is obvious that the drawings described below are merely some embodiments of this application, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort. In the drawings: Figure 1 This is a schematic diagram of the structure of a temperature control system provided in one embodiment of this application.

[0030] Figure 2 This is a schematic diagram of the structure of a temperature control system provided in another embodiment of this application.

[0031] Figure 3 This is a schematic diagram of the operation of a temperature control system in cooling mode according to an embodiment of this application.

[0032] Figure 4 This is a flowchart of the steps that the control unit can execute, provided in one embodiment of this application.

[0033] Figure 5 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0034] Figure 6 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0035] Figure 7 This is a schematic diagram of the operation of a temperature control system in cooling mode according to an embodiment of this application.

[0036] Figure 8 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0037] Figure 9 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0038] Figure 10 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0039] Explanation of reference numerals in the attached drawings: 1: First heat exchanger; 2: Compressor; 3: Second heat exchanger; 4: First expansion valve; 5: Compressor drive module; 6: Drive liquid cooling plate; 7: Third heat exchanger; 8: Drive device; 9: Battery liquid cooling assembly; 10: First four-way valve; 11: Second four-way valve; 12: Second expansion valve; 13: Three-way valve; 14: Flow regulating valve; 15: Drive liquid cooling plate temperature sensor; 16: Compressor drive module temperature sensor; 17: Compressor suction temperature sensor; 18: Compressor suction pressure sensor; 19: Discharge temperature sensor. Detailed Implementation

[0040] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims.

[0041] The flowcharts shown in the accompanying drawings are merely illustrative and do not necessarily include all content and operations / steps, nor do they necessarily need to be executed in the described order. For example, some operations / steps can be broken down, while others can be combined or partially combined; therefore, the actual execution order may change depending on the actual situation. It should also be noted that "multiple" as mentioned in this application refers to two or more. "And / or" describes the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. The character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0042] The terms "first," "second," "third," and "fourth," etc., in the specification, claims, and drawings of this application are used to distinguish different objects, not to describe a specific order. The terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0043] When a structural element is mentioned as being "connected" or "in contact" with another structural element, it may mean that it is directly connected to or in contact with the other structural element, but it can also be understood as meaning that there are other structural elements between them. Conversely, when a structural element is mentioned as being "directly connected" or "directly in contact" with another structural element, it should be understood as meaning that there are no other structural elements between them.

[0044] Unless the context clearly indicates a different meaning, the singular form includes the plural form.

[0045] As the energy storage industry develops on a large scale, the demand for heat dissipation from energy storage batteries continues to increase, leading to a corresponding increase in the cooling capacity requirement for temperature control units. To match the higher cooling capacity output, the temperature control system needs to be equipped with compressors that have higher power consumption and larger displacement. As the core control component, the heat load generated by the compressor drive module increases significantly with the increase in compressor power.

[0046] To address the heat dissipation requirements of the compressor drive module, traditional energy storage temperature control systems generally employ air cooling. This method uses a fan to force airflow away heat from the surface of the compressor drive module, maintaining its temperature within a certain range.

[0047] However, with the increase in compressor power and the increase in the heat load of compressor drive modules, the drawbacks of traditional air-cooling heat dissipation methods have become increasingly apparent. Their heat dissipation capacity has a clear upper limit and is difficult to meet the heat dissipation requirements of current high-power compressor drive modules.

[0048] To address the aforementioned technical problems, this application proposes a temperature control system capable of effectively dissipating heat from the compressor drive module.

[0049] Figure 1 This is a schematic diagram of the structure of a temperature control system provided in one embodiment of this application. Figure 2 This is a schematic diagram of the structure of a temperature control system provided in another embodiment of this application.

[0050] The temperature control system will be described in detail below.

[0051] See Figure 1 , Figure 2 As shown, in some embodiments, the temperature control system may include a refrigerant circulation subsystem. The internal circulating working fluid of the refrigerant circulation subsystem is a refrigerant, which may be R410A, R134a, or R290.

[0052] In some embodiments, the refrigerant circulation subsystem may further include a first heat exchanger 1. The first heat exchanger 1 is used to exchange heat between the refrigerant flowing through it and the air. The inlet end of the first heat exchanger 1 is connected to the third port of the first four-way valve 10, the second port of the three-way valve 13, and one end of the third heat exchanger 7, and the outlet end is connected to the first port of the second four-way valve 11. The first heat exchanger 1 may be a finned tube condenser, a plate-fin condenser, or a parallel flow microchannel condenser, with outdoor air and refrigerant on its two sides, respectively. In cooling mode, it acts as a condenser, where outdoor air absorbs heat and rises in temperature, and the refrigerant, under high pressure, releases heat and condenses. In heating mode, it acts as an evaporator, where outdoor air releases heat and cools down, and the refrigerant, under low pressure, absorbs heat and evaporates. In addition to the aforementioned air-cooled heat exchange condenser, the first heat exchanger 1 may also be of other heat exchange forms, including but not limited to cooling tower heat exchange, indirect evaporative cooling heat exchange, etc.

[0053] In some embodiments, the refrigerant circulation subsystem may further include a fan. The fan is located on the side of the first heat exchanger 1 and can drive an impeller to rotate, causing air to be blown toward the first heat exchanger 1.

[0054] In some embodiments, the refrigerant cycle subsystem may include compressor 2. Compressor 2 is the power core of the refrigerant cycle subsystem, used to compress the refrigerant, compressing the refrigerant flowing out of the second port of the second four-way valve 11 into a high-temperature, high-pressure gaseous refrigerant, providing power for the refrigerant phase change cycle. Compressor 2 may be a coupled compressor. Compressor 2 may be a scroll compressor. Compressor 2 may be of other types.

[0055] In some embodiments, the temperature control system may further include a second heat exchanger 3. One end of the refrigerant side is connected to the first port of the first four-way valve 10, and the other end is connected to the third port of the second four-way valve 11; the coolant side forms a loop with the outlet end of the drive device 8 and the battery liquid cooling assembly 9. The refrigerant flowing out from the first port flows sequentially through the second heat exchanger 3 to the third port, where it exchanges heat with the coolant flowing out from the outlet end of the drive device 8 in the second heat exchanger 3.

[0056] In some embodiments, the refrigerant cycle subsystem may further include a first expansion valve 4. The two ends of the first expansion valve 4 are connected to a second interface and a fourth port, respectively. The first expansion valve 4 is the core of the refrigerant cycle subsystem for throttling and pressure reduction, employing throttling and pressure reduction technology to convert the high-pressure liquid refrigerant in the circuit into a low-pressure gas-liquid two-phase state. The first expansion valve 4 can be an electronic expansion valve for precise control of the refrigerant flow rate.

[0057] In some embodiments, the temperature control system may include a coolant circulation subsystem. The internal circulating medium of the coolant circulation subsystem is coolant, which may be an aqueous solution of ethylene glycol with a volume concentration of 20%-30%, taking into account antifreeze properties, thermal conductivity, and corrosiveness.

[0058] In some embodiments, the coolant circulation subsystem may include a compressor drive module 5. The compressor drive module 5 is the control core of the compressor 2, electrically connected to the compressor 2, and is used to drive the compressor 2. Specifically, it outputs a variable frequency drive signal to control the operating frequency of the compressor 2. Simultaneously, the compressor drive module 5 itself generates a heat load as the power of the compressor 2 increases.

[0059] In some embodiments, the coolant circulation subsystem may include a drive liquid cooling plate 6. The drive liquid cooling plate 6 is the heat dissipation core of the compressor drive module 5, is disposed in close contact with the compressor drive module 5, and is used to allow the coolant flowing through it to exchange heat with the compressor drive module 5, thereby removing the heat generated by the compressor drive module 5 through the internal coolant flow.

[0060] In some embodiments, the temperature control system may further include a third heat exchanger 7. One end of the refrigerant side is connected to the third port of the three-way valve 13, and the other end is connected to the inlet end of the first heat exchanger 1; the coolant side forms a circuit with the outlet end of the drive unit 8 and the flow regulating valve 14. The refrigerant flowing out of the outlet end of the compressor 2 flows through the second expansion valve 12, the first port, the third port and the third heat exchanger 7 to the inlet end of the first heat exchanger 1, where it exchanges heat with the coolant flowing out of the outlet end of the drive unit 8 in the third heat exchanger 7.

[0061] In some embodiments, the coolant circulation subsystem may include a drive unit 8. The drive unit 8 is the power core of the coolant circulation subsystem, used to drive the coolant circulation flow. The inlet end of the drive unit 8 is connected to the outlet end of the battery liquid cooling assembly 9. The drive unit 8 may be a water pump. The drive unit 8 may be a positive displacement pump. The drive unit 8 may be a self-priming pump. Other types of drive units may also be used.

[0062] In some embodiments, the coolant circulation subsystem may include a battery liquid cooling assembly 9. The battery liquid cooling assembly 9 is the core of temperature control for the energy storage battery, consisting of multiple battery liquid cooling modules. It regulates the temperature of the energy storage battery by exchanging heat with the internal coolant. Multiple battery liquid cooling modules can be connected in parallel for more uniform flow. Alternatively, multiple battery liquid cooling modules can be connected in series for more thorough heat exchange.

[0063] In some embodiments, the refrigerant circulation subsystem may further include a first four-way valve 10. By switching the position of the internal slide valve of the first four-way valve 10, the refrigerant circuit can be reconfigured in cooling / heating mode. The first four-way valve 10 has a first interface, a second interface, a third interface, and a fourth interface. The third interface is connected to the inlet end of the first heat exchanger 1, and the fourth interface is connected to the outlet end of the compressor 2.

[0064] In some embodiments, the refrigerant circulation subsystem may further include a second four-way valve 11. By switching the position of the internal slide valve of the second four-way valve 11, the refrigerant circuit can be reconfigured in cooling / heating mode. The second four-way valve 11 has a first port, a second port, a third port, and a fourth port. The first port is connected to the outlet end of the first heat exchanger 1, and the second port is connected to the inlet end of the compressor 2.

[0065] In some embodiments, the refrigerant cycle subsystem may further include a second expansion valve 12. One end of the second expansion valve 12 is connected to the outlet end of the compressor 2, and the other end is connected to the first port of the three-way valve 13. The second expansion valve 12 is the core of the refrigerant cycle subsystem for throttling and pressure reduction. It uses throttling and pressure reduction technology to convert the high-pressure liquid refrigerant in the circuit into a low-pressure gas-liquid two-phase state. The second expansion valve 12 can be an electronic expansion valve to precisely control the refrigerant flow rate.

[0066] In some embodiments, the refrigerant circulation subsystem may further include a three-way valve 13. By switching the connection state of the internal port of the three-way valve 13, the flow path of the waste heat utilization branch can be changed. The three-way valve 13 has a first port, a second port, and a third port. The first port is connected to the other end of the second expansion valve 12, and the second port is connected to the inlet end of the first heat exchanger 1.

[0067] In some embodiments, the coolant circulation subsystem may include a flow control valve 14. The flow control valve 14 is the core component for regulating the flow of the driving liquid cooling plate 6, used to precisely regulate the flow rate of the coolant flowing through it, thereby controlling the heat exchange efficiency and surface temperature of the driving liquid cooling plate 6. The flow control valve 14 may be an electrically operated proportional control valve with an adjustment range of 0%-100% opening.

[0068] In some embodiments, the coolant circulation subsystem may include a drive liquid cooling plate temperature sensor 15. The drive liquid cooling plate temperature sensor 15 is a core detection component for anti-condensation control, used to detect the surface temperature of the drive liquid cooling plate 6 in real time.

[0069] In some embodiments, the coolant circulation subsystem may include a compressor drive module temperature sensor 16. The compressor drive module temperature sensor 16 is a core detection component for the protection of the compressor drive module 5 and can be used to detect the operating temperature of the compressor drive module 5 in real time.

[0070] In some embodiments, the refrigerant cycle subsystem may further include a compressor suction temperature sensor 17. The compressor suction temperature sensor 17 is the core of the refrigerant cycle status monitoring system, used to detect the suction temperature of the compressor 2 in real time, providing basic data for calculating the suction superheat of the compressor 2.

[0071] In some embodiments, the refrigerant circulation subsystem may further include a compressor suction pressure sensor 18. The compressor suction pressure sensor 18 is the core of the refrigerant circulation status monitoring system, used to detect the suction pressure of the compressor 2 in real time, providing basic data for calculating the evaporation temperature of the compressor 2.

[0072] In some embodiments, the coolant circulation subsystem may include an outlet temperature sensor 19. The outlet temperature sensor 19 is disposed at the outlet end of the battery liquid cooling assembly 9 and is used to detect the outlet temperature of the energy storage battery in real time, reflecting the actual thermal state of the energy storage battery.

[0073] In some embodiments, the temperature control system may further include a control unit.

[0074] Figure 3 This is a schematic diagram of the operation of a temperature control system in cooling mode according to an embodiment of this application. Figure 3 As shown, in some embodiments of this application, the control unit can be configured to perform the following S110: S110, when the temperature control system is operating in cooling mode, the second port is closed, and the refrigerant flowing from the compressor outlet flows sequentially through the fourth port, the third port, the first heat exchanger, the first port, the fourth port, the first expansion valve, the second port, the first port, the second heat exchanger, the third port, and the second port to the compressor inlet, thus forming the first refrigerant main circuit; and The refrigerant flowing out from the compressor outlet flows sequentially through the second expansion valve, the first port, the third port, the third heat exchanger, and the first heat exchanger to form the first refrigerant waste heat utilization branch.

[0075] In the S110, the cooling mode is the main heat dissipation mode of the temperature control system. It generates continuous and stable cooling capacity through the phase change cycle of the refrigerant, and then the coolant accurately transfers the cooling capacity to the energy storage battery and compressor drive module, solving the pain points of insufficient heat dissipation capacity of traditional air cooling and direct heat dissipation of refrigerant interfering with the stability of the temperature control system.

[0076] In some embodiments, when the temperature control system operates in cooling mode, the slide valve of the three-way valve can be controlled to switch to the cooling position, opening the first and third ports and closing the second port. When the temperature control system operates in cooling mode, the first interface of the first four-way valve can also be connected to the second interface, and the third interface to the fourth interface; the first port of the second four-way valve can be connected to the fourth port, and the second port to the third port. Thus, the refrigerant flowing from the compressor outlet flows sequentially through the fourth interface, the third interface, the first heat exchanger, the first port, the fourth port, the first expansion valve, the second interface, the first interface, the second heat exchanger, the third port, and the second port to the compressor inlet, forming the first refrigerant main circuit. The refrigerant flowing from the compressor outlet flows sequentially through the second expansion valve, the first port, the third port, the third heat exchanger, and the first heat exchanger, forming the first refrigerant waste heat utilization branch.

[0077] The first refrigerant main circuit includes: a first heat exchanger, a compressor, a second heat exchanger, a first expansion valve, a first four-way valve, and a second four-way valve. The first refrigerant waste heat utilization branch includes: a second expansion valve, a three-way valve, and a third heat exchanger.

[0078] Figure 4 This is a flowchart of the steps that the control unit can execute, provided in one embodiment of this application.

[0079] See Figure 4 As shown, in some embodiments of this application, the control unit can be configured to perform the following steps S210-S220: S210: When the temperature control system is running in cooling mode, the control flow regulating valve is fully open and the second expansion valve is fully closed.

[0080] S220, if the surface temperature of the driving liquid cooling plate is detected to be below the set temperature of the driving liquid cooling plate, the second expansion valve is adjusted to make the surface temperature of the driving liquid cooling plate reach the set temperature of the driving liquid cooling plate, wherein the set temperature of the driving liquid cooling plate is determined based on the dew point temperature inside the electrical control box and is greater than the dew point temperature inside the electrical control box.

[0081] S210-S220 will be described in detail below.

[0082] In S210, when the temperature control system is running in cooling mode, the flow regulating valve is fully opened to maximize the flow of coolant through the drive liquid cooling plate, thereby maximizing the removal of the dynamic heat load of the compressor drive module and preventing heat accumulation due to insufficient coolant flow. The second expansion valve is also fully closed to cut off the refrigerant flow in the first refrigerant waste heat utilization branch, preventing refrigerant diversion in the first refrigerant main circuit and ensuring that the cooling efficiency of the first refrigerant main circuit is not disturbed.

[0083] In S220, if the surface temperature of the drive liquid cooling plate is detected to be below the set temperature (determined based on the dew point temperature inside the control box and is higher than the set temperature), indicating that condensation is imminent, the second expansion valve is adjusted to bring the surface temperature of the drive liquid cooling plate back to the set temperature. This temperature compensation effectively prevents condensation, balancing condensation prevention and heat dissipation efficiency, and avoiding damage to the control system such as insulation degradation and short circuits. The dew point temperature inside the control box can be calculated by measuring the dry-bulb temperature and relative humidity. The dry-bulb temperature can be measured by a temperature sensor inside the control box, and the relative humidity can be measured by a humidity sensor inside the control box.

[0084] By detecting the difference between the surface temperature of the drive liquid cooling plate and the dew point temperature inside the electrical control box, the second expansion valve is adjusted for precise temperature compensation, ensuring that the surface temperature of the drive liquid cooling plate is always higher than the dew point temperature inside the electrical control box, thus completely eliminating condensation (condensation can lead to short circuits in the electrical control and deterioration of the drive module's insulation), while not affecting the normal heat dissipation of the compressor drive module.

[0085] In some embodiments, the relationship between the set temperature of the drive liquid cooling plate and the dew point temperature inside the electrical control box can be expressed by the following formula: Tsuf < Tdew + 3; Tsuf = Tdew + 3 Where Tsuf represents the surface temperature of the driving liquid cooling plate, Tdew+3 represents the set temperature of the driving liquid cooling plate, and Tdew represents the dew point temperature inside the electrical control box; Tsuf < Tdew+3 indicates that the surface temperature of the driving liquid cooling plate is below the set temperature of the driving liquid cooling plate; Tsuf = Tdew+3 indicates that the surface temperature of the driving liquid cooling plate reaches the set temperature of the driving liquid cooling plate; 3 represents the difference between the set temperature of the driving liquid cooling plate and the dew point temperature inside the electrical control box.

[0086] It should be noted that the difference between the set temperature of the driving liquid cooling plate and the dew point temperature inside the electrical control box can also be other values, and this embodiment does not limit this.

[0087] Figure 5 This is a flowchart of the steps that the control unit can execute, provided in one embodiment of this application.

[0088] See Figure 5 As shown, in some embodiments of this application, the control unit can be configured to perform the following steps S310-S320: S310, if the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, the surface temperature of the drive liquid cooling plate is maintained at the set temperature of the drive liquid cooling plate, and the opening degree of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve; wherein, the set temperature of the compressor drive module is determined according to the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module.

[0089] S320: When the operating temperature of the compressor drive module is detected to reach the set temperature of the compressor drive module or the second expansion valve is fully closed, the flow regulating valve and the second expansion valve will be stopped.

[0090] The following sections will elaborate on these two steps.

[0091] In S310, if the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, it indicates that the heat load of the compressor drive module is lower than the current heat dissipation capacity, and the temperature safety redundancy is sufficient. The set temperature of the compressor drive module is determined based on the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module.

[0092] In some embodiments, the relationship between the operating temperature of the compressor drive module and the set temperature of the compressor drive module can be expressed by the following formula: Td < Td,max - 5; Td = Td,max - 5 Where Td represents the operating temperature of the compressor drive module; Td,max-5 represents the set temperature of the compressor drive module; Td,max represents the maximum operating temperature of the compressor drive module; Td<Td,max-5 indicates that the operating temperature of the compressor drive module is below the set temperature of the compressor drive module; Td=Td,max-5 indicates that the surface temperature of the drive liquid cooling plate reaches the set temperature of the drive liquid cooling plate; and 5 represents the difference between the set temperature of the compressor drive module and the maximum operating temperature of the compressor drive module.

[0093] It should be noted that the difference between the set temperature of the compressor drive module and the maximum operating temperature of the compressor drive module can also be other values, and this embodiment does not limit this.

[0094] If the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, the surface temperature of the drive liquid cooling plate achieved by S220 is maintained at the set temperature of the drive liquid cooling plate, and the opening degree of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve.

[0095] In S320, when the operating temperature of the compressor drive module is detected to have reached the set temperature of the compressor drive module, the adjustment of the flow control valve and the second expansion valve can be stopped, i.e., the opening of the flow control valve and the second expansion valve can be maintained. Similarly, when the second expansion valve is detected to be fully closed, the adjustment of the flow control valve and the second expansion valve can also be stopped, i.e., the opening of the flow control valve and the second expansion valve can be maintained.

[0096] As shown in S310 above, if the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, where the set temperature of the compressor drive module is determined based on the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module, it indicates that the heat load of the compressor drive module is lower than the current heat dissipation capacity and the temperature safety redundancy is sufficient. In this case, the surface temperature of the drive liquid cooling plate is maintained at the set temperature of the drive liquid cooling plate, and the opening of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve. When the operating temperature of the compressor drive module is detected to reach the set temperature of the compressor drive module or the second expansion valve is fully closed, the adjustment of the flow regulating valve and the second expansion valve is stopped. Thus, based on preventing condensation and ensuring heat dissipation, the energy waste problem caused by the fixed control mode is solved through fine control.

[0097] Figure 6 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0098] See Figure 6 As shown, in some embodiments of this application, the control unit can be configured to perform the following steps S410-S420: S410: If the surface temperature of the driving liquid cooling plate is detected to be above the set temperature of the driving liquid cooling plate, the opening of the flow regulating valve and the second expansion valve shall be maintained.

[0099] S420: If the operating temperature of the compressor drive module is detected to be above the set temperature of the compressor drive module, the opening of the flow regulating valve and the second expansion valve shall be maintained.

[0100] S410-S420 will be described in detail below.

[0101] In S410, if the surface temperature of the driving liquid cooling plate is detected to be above the set temperature of the driving liquid cooling plate, it indicates that the coolant will not condense. Therefore, the opening of the flow regulating valve and the opening of the second expansion valve are maintained to avoid frequent parameter fluctuations and improve the operational stability of the temperature control system.

[0102] In S420, if the operating temperature of the compressor drive module is detected to be above the set temperature of the compressor drive module, it indicates that the heat load of the compressor drive module has approached the current heat dissipation capacity. Therefore, the opening of the flow regulating valve and the opening of the second expansion valve are maintained to avoid frequent parameter fluctuations and improve the operational stability of the temperature control system.

[0103] In other embodiments, if a change in the compressor's operating frequency is detected, causing the surface temperature of the driving liquid cooling plate to fall below the set temperature of the driving liquid cooling plate, the flow regulating valve can be fully opened and the second expansion valve fully closed. If the surface temperature of the driving liquid cooling plate is detected to be below the set temperature of the driving liquid cooling plate, the second expansion valve is adjusted to bring the surface temperature of the driving liquid cooling plate up to the set temperature of the driving liquid cooling plate. The set temperature of the driving liquid cooling plate is determined based on and is greater than the dew point temperature inside the electrical control box. If the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, the surface temperature of the driving liquid cooling plate is maintained at the set temperature of the driving liquid cooling plate, and the opening degree of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve. The set temperature of the compressor drive module is determined based on and is less than the maximum operating temperature of the compressor drive module.

[0104] In other embodiments, if a change in the compressor's operating frequency is detected, causing the compressor drive module's operating temperature to reach or exceed the compressor drive module's set temperature, the flow regulating valve can be fully opened and the second expansion valve fully closed. If the surface temperature of the drive liquid cooling plate is detected to be below the drive liquid cooling plate's set temperature, the second expansion valve is adjusted to bring the drive liquid cooling plate's surface temperature up to the drive liquid cooling plate's set temperature. The drive liquid cooling plate's set temperature is determined based on and is greater than the dew point temperature inside the electrical control box. If the compressor drive module's operating temperature is detected to be below the compressor drive module's set temperature, the drive liquid cooling plate's surface temperature is maintained at the drive liquid cooling plate's set temperature, and the opening degree of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve. The compressor drive module's set temperature is determined based on and is less than the compressor drive module's maximum operating temperature.

[0105] In other embodiments, if the operating temperature of the compressor drive module is detected to be above the maximum operating temperature of the compressor drive module, the compressor can be controlled to operate at a reduced frequency.

[0106] Figure 7 This is a schematic diagram of the operation of a temperature control system in cooling mode according to an embodiment of this application. Figure 7 As shown, in some embodiments of this application, the control unit can be configured to execute the following S510: S510, when the temperature control system is operating in heating mode, the third port is closed, and the refrigerant flowing from the compressor outlet flows sequentially through the fourth port, the first port, the second heat exchanger, the third port, the fourth port, the first expansion valve, the second port, the third port, the first heat exchanger, the first port, and the second port to the compressor inlet, thus forming the second refrigerant main circuit; and The refrigerant flowing out from the compressor outlet flows sequentially through the second expansion valve, the first port, the second port, and the first heat exchanger to form the second refrigerant waste heat utilization branch.

[0107] In the S510, the heating mode is the core operating mode designed for scenarios where energy storage battery performance degrades and cannot start / operate normally in low-temperature environments. When the temperature control system operates in heating mode, it can control the slide valve of the three-way valve to switch to the heating position, opening the first and second ports and closing the third port. When the temperature control system operates in heating mode, it can also control the first and fourth ports of the first four-way valve to connect, and the second and third ports to connect; the first and second ports of the second four-way valve to connect, and the third and fourth ports to connect. Thus, the refrigerant flowing from the compressor outlet flows sequentially through the fourth port, the first port, the second heat exchanger, the third port, the fourth port, the first expansion valve, the second port, the third port, the first heat exchanger, the first port, and the second port to the compressor inlet, forming the second refrigerant main circuit. The refrigerant flowing from the compressor outlet flows sequentially through the second expansion valve, the first port, the second port, and the first heat exchanger, forming the second refrigerant waste heat utilization branch.

[0108] The second refrigerant main circuit includes: a first heat exchanger, a compressor, a second heat exchanger, a first expansion valve, a first four-way valve, and a second four-way valve. The second refrigerant waste heat utilization branch includes: a second expansion valve, a three-way valve, and a third heat exchanger.

[0109] In some embodiments of this application, the control unit may be configured to perform the following S610: S610, when the temperature control system is running in heating mode, controls the flow regulating valve to be fully open and controls the opening of the second expansion valve to be in a half-open and half-closed state to defrost the outer surface of the first heat exchanger.

[0110] Furthermore, when the temperature control system operates in heating mode, the flow regulating valve is fully open, allowing the coolant to flow through the drive liquid cooling plate at maximum flow rate, quickly removing heat and preventing the drive module temperature from exceeding the maximum allowable limit, thus ensuring stable compressor operation. When the temperature control system operates in heating mode, the second expansion valve is also controlled to be in a partially open / closed state, precisely distributing the hot gas flow from the compressor exhaust to achieve non-stop defrosting of the outer surface of the first heat exchanger, ensuring refrigerant flow efficiency and the heat exchange efficiency of the first heat exchanger. Once defrosting of the outer surface of the first heat exchanger is complete, the second expansion valve can be fully closed.

[0111] In some embodiments, the second expansion valve is in a partially open state, i.e., the opening degree is between 10% and 90%. The opening degree can also be other values.

[0112] Figure 8 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0113] See Figure 8 As shown, in some embodiments of this application, the control unit can be configured to execute the following S710-S750: S710 determines the compressor evaporation temperature based on the compressor suction pressure.

[0114] S720 calculates the compressor suction superheat based on the compressor suction temperature and the compressor evaporation temperature.

[0115] S730 calculates the difference in compressor suction superheat based on the compressor suction superheat and the target compressor suction superheat.

[0116] S740, obtains the adjustment coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference.

[0117] S750 adjusts the opening of the first expansion valve based on the adjustment coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference.

[0118] The following sections will elaborate on S710-S750 respectively.

[0119] In the S710, the compressor evaporation temperature can be accurately derived by the correspondence between the compressor suction pressure and the compressor evaporation temperature. This provides core parameters for subsequent suction superheat calculation and expansion valve opening adjustment, ensuring that the refrigerant circulation and coolant cooling capacity requirements are matched.

[0120] In the S720, the suction superheat reflects the degree to which the refrigerant evaporates within the heat exchanger (insufficient superheat may lead to liquid slugging, while excessive superheat will reduce heat exchange efficiency).

[0121] In some embodiments, the compressor suction superheat can be equal to the difference between the compressor suction temperature and the compressor evaporation temperature.

[0122] In S730, in some embodiments, the compressor suction superheat difference can be equal to the difference between the compressor suction superheat and the target compressor suction superheat.

[0123] In the S740, the regulation coefficient can be the proportional-integral-derivative (PID) regulation constant for the expansion valve opening. The historical compressor suction superheat difference can be the compressor suction superheat difference from the previous cycle. Alternatively, the historical compressor suction superheat difference can also be the compressor suction superheat difference from the previous cycle.

[0124] In S750, in some embodiments, the opening degree of the first expansion valve can be adjusted according to the following formula: E(k) = E(k-1) + ΔE △E = Kpe×[ e(k)- e(k-1) ] + Kie×e(k) Wherein, E(k) is the opening degree of the first expansion valve; E(k-1) is the opening degree of the first expansion valve in the previous cycle; ΔE is the PID calculation adjustment value of the opening degree of the first expansion valve; e(k) is the current compressor suction superheat difference, i.e., the measured compressor suction superheat minus the target compressor suction superheat; e(k-1) is the compressor suction superheat difference in the previous cycle; Kpe and Kie are the PID adjustment constants of the opening degree of the first expansion valve, which can be determined through debugging.

[0125] As can be seen from S710-S750 above, the opening of the first expansion valve is precisely adjusted by adjusting the coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference, so as to avoid compressor failure caused by abnormal compressor suction superheat.

[0126] Figure 9 This is a flowchart of the steps that the control unit can execute, provided in another embodiment of this application.

[0127] See Figure 9 As shown, in some embodiments of this application, the control unit can be configured to execute the following S810-S820: S810: If the detected energy storage battery outlet temperature reaches or exceeds the first target energy storage battery outlet temperature, the temperature control system will be controlled to operate in cooling mode.

[0128] S820 If the detected energy storage battery outlet temperature is below the second target energy storage battery outlet temperature, the temperature control system will stop operating the cooling mode, and the second target energy storage battery outlet temperature will be lower than the first target energy storage battery outlet temperature.

[0129] The following sections will elaborate on S810-S820 respectively.

[0130] In the S810, if the detected liquid temperature of the energy storage battery reaches or exceeds the first target liquid temperature, it indicates that the current temperature of the energy storage battery is too high. The system then precisely controls the temperature control system to operate in cooling mode. Using the liquid temperature of the energy storage battery (which directly reflects the actual thermal state of the battery) as the sole criterion, the system ensures that the cooling mode is only activated when the energy storage battery truly needs active cooling, avoiding energy waste and unnecessary component wear caused by unnecessarily operating the system.

[0131] In the S820, if the detected outlet temperature of the energy storage battery is below the second target outlet temperature, it indicates that the current temperature of the energy storage battery is not high. Therefore, the temperature control system is precisely controlled to stop the cooling mode. The second target outlet temperature is lower than the first target outlet temperature. By setting a "second target temperature lower than the first target temperature," a "temperature lag range" is formed, avoiding frequent start-stop of the cooling mode due to small fluctuations in the outlet temperature of the energy storage battery (frequent start-stop of core components will accelerate wear and shorten their lifespan).

[0132] In some embodiments, the relationship between the liquid outlet temperature of the first target energy storage battery and the liquid outlet temperature of the second target energy storage battery can be expressed by the following formula: Tout,1 = Tout,2 + 2.5 Wherein, Tout,1 represents the first target energy storage battery outlet temperature, Tout,2 represents the second target energy storage battery outlet temperature, and 2.5 represents the difference between the first target energy storage battery outlet temperature and the second target energy storage battery outlet temperature.

[0133] It should be noted that the difference between the liquid outlet temperature of the first target energy storage battery and the liquid outlet temperature of the second target energy storage battery can also be other values, and this embodiment does not limit this.

[0134] Figure 10 This is a flowchart of the steps that the control unit can execute, provided in one embodiment of this application.

[0135] See Figure 10 As shown, in some embodiments of this application, the control unit can be configured to execute the following S910-S920: S910: If the temperature of the energy storage battery outlet is detected to be below the third target energy storage battery outlet temperature, the temperature control system will be controlled to operate in heating mode.

[0136] S920: If the detected energy storage battery outlet temperature reaches or exceeds the second target energy storage battery outlet temperature, the temperature control system will stop operating the heating mode. The third target energy storage battery outlet temperature will be lower than the second target energy storage battery outlet temperature.

[0137] The S910-S920 will be described in detail below.

[0138] In the S910, if the detected outlet temperature of the energy storage battery is below the third target outlet temperature, it indicates that the current temperature of the energy storage battery is too low. The system then precisely controls the temperature control system to operate in heating mode. Using the outlet temperature of the energy storage battery (which directly reflects the thermal state of the battery) as the sole criterion, the system ensures that the heating mode is only activated when the battery's performance degrades or fails to start due to low temperatures. This avoids energy waste caused by unnecessary heating and also adapts to the low-temperature preheating needs of batteries in extremely cold environments.

[0139] In the S920, if the detected energy storage battery outlet temperature reaches or exceeds the second target energy storage battery outlet temperature, it indicates that the current temperature of the energy storage battery is not low, and the temperature control system is precisely controlled to stop the heating mode. The third target energy storage battery outlet temperature is lower than the second target energy storage battery outlet temperature. By setting a second target temperature higher than the third target temperature, a "temperature lag range" is formed to avoid frequent start-stop of the heating mode due to small fluctuations in the battery outlet temperature (frequent start-stop of the heater / compressor will accelerate component aging and cause unstable heat supply).

[0140] In some embodiments, the relationship between the liquid outlet temperature of the second target energy storage battery and the liquid outlet temperature of the third target energy storage battery can be expressed by the following formula: Tout,2 = Tout,3 + 2.5 Where Tout,2 represents the second target energy storage battery outlet temperature, Tout,3 represents the third target energy storage battery outlet temperature, and 2.5 represents the difference between the second target energy storage battery outlet temperature and the third target energy storage battery outlet temperature.

[0141] It should be noted that the difference between the liquid outlet temperature of the second target energy storage battery and the liquid outlet temperature of the third target energy storage battery can also be other values, and this embodiment does not limit this.

[0142] Based on the above technical solution, the embodiments of the present invention have the following advantages and positive effects: The coolant circulation subsystem includes a drive liquid cooling plate, which is attached to the compressor drive module. The coolant flowing through the drive liquid cooling plate exchanges heat with the compressor drive module. Compared with air cooling, liquid cooling has stronger heat dissipation capacity and higher heat dissipation efficiency, solving the technical problems of insufficient heat dissipation capacity and weak heat dissipation efficiency of traditional air cooling.

[0143] The temperature control system is divided into a refrigerant circulation subsystem and a coolant circulation subsystem, separating the refrigerant circulation loop from the coolant circulation loop. Heat exchange is achieved only through a heat exchanger, without direct medium mixing or loop interconnection, ensuring the operational stability of the temperature control system. Furthermore, heat exchange is conducted between the coolant and the compressor drive module. Since the coolant is a single-phase fluid with no phase change process, its temperature change is gradual, further ensuring the operational stability of the temperature control system. This solves the technical problem of system instability caused by using refrigerant to dissipate heat from the compressor drive module.

[0144] After the refrigerant is compressed by the compressor, a high-temperature refrigerant is obtained. This high-temperature refrigerant flows sequentially through the second expansion valve, the first port, the third port, and the third heat exchanger. In the third heat exchanger, it exchanges heat with the coolant flowing out of the drive unit's outlet. By utilizing the waste heat from the compressor exhaust, the surface temperature of the drive liquid cooling plate can be increased with lower energy consumption compared to electric heating, thus preventing condensation on the drive liquid cooling plate. The high-temperature refrigerant, obtained by the compressor compression, flows sequentially through the second expansion valve, the first port, the second port, and finally to the first heat exchanger. Utilizing the waste heat from the compressor exhaust solves the high energy consumption problem caused by electric heating.

[0145] When the temperature control system operates in cooling mode, the flow regulating valve is fully open to maximize the flow of coolant through the drive liquid cooling plate, thereby maximizing the removal of dynamic heat load from the compressor drive module and preventing heat accumulation due to insufficient coolant flow. Simultaneously, the second expansion valve is fully closed to cut off refrigerant flow in the first refrigerant waste heat utilization branch, preventing refrigerant diversion in the first refrigerant main circuit and ensuring uninterrupted cooling efficiency. If the surface temperature of the drive liquid cooling plate is detected to be below the set temperature (determined based on the dew point temperature inside the control box and is higher than this temperature), indicating impending condensation, the second expansion valve is adjusted to bring the surface temperature of the drive liquid cooling plate up to the set temperature. This replenishes the temperature of the drive liquid cooling plate, preventing coolant condensation. This effectively balances condensation prevention and heat dissipation efficiency, while mitigating potential damage to the electrical control system, such as insulation degradation and short circuits.

[0146] If the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module (where the set temperature is determined based on the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module), it indicates that the heat load of the compressor drive module is lower than the current heat dissipation capacity and the temperature safety redundancy is sufficient. In this case, the surface temperature of the drive liquid cooling plate is maintained at the set temperature of the drive liquid cooling plate, and the opening of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve. When the operating temperature of the compressor drive module is detected to reach the set temperature of the compressor drive module or the second expansion valve is fully closed, the adjustment of the flow regulating valve and the second expansion valve is stopped. Thus, based on preventing condensation and ensuring heat dissipation, the energy waste problem caused by the fixed control mode is solved through fine control.

[0147] If the surface temperature of the driving liquid cooling plate is detected to be above the set temperature of the driving liquid cooling plate, it indicates that the coolant will not condense. Therefore, the opening of the flow control valve and the second expansion valve should be maintained to avoid frequent parameter fluctuations and improve the operational stability of the temperature control system. If the operating temperature of the compressor drive module is detected to be above the set temperature of the compressor drive module, it indicates that the heat load of the compressor drive module has approached its current heat dissipation capacity. Therefore, the opening of the flow control valve and the second expansion valve should be maintained to avoid frequent parameter fluctuations and improve the operational stability of the temperature control system.

[0148] When the temperature control system is running in heating mode, the flow regulating valve is fully open, allowing the coolant to flow through the drive liquid cooling plate at maximum flow rate, quickly removing heat and preventing the drive module temperature from exceeding the maximum allowable limit, thus ensuring stable compressor operation. Additionally, the second expansion valve is controlled to be in a semi-open / semi-closed state, precisely distributing the hot gas flow from the compressor exhaust, enabling continuous defrosting of the outer surface of the first heat exchanger, ensuring refrigerant flow efficiency and the heat exchange efficiency of the first heat exchanger.

[0149] The preferred embodiments of the present invention have been illustrated and described above. However, the present invention is not limited to the specific embodiments described above. Of course, those skilled in the art can make various modifications without departing from the spirit of the invention as claimed in the claims. These modifications should not be understood separately from the technical concept or prospect of the present invention.

[0150] This invention can be implemented in various forms, and its scope of claim is not limited to the embodiments described above. Therefore, any modified embodiment that includes the constituent elements within the scope of the claims of this invention should be considered to fall within the scope of the claims of this invention.

[0151] The embodiments of the present invention described above, or other embodiments thereof, are not mutually exclusive or distinct. The embodiments of the present invention described above, or other embodiments thereof, can be used in combination or in combination of their respective configurations or functions.

[0152] For example, it indicates that configuration A described in a particular embodiment and / or figure and configuration B described in another embodiment and / or figure can be combined. That is, even if no combination between the configurations is directly described, it indicates that they can be combined, except where cases where combination is impossible are explained.

[0153] The detailed description above should not be construed as limiting in all respects, but should be considered exemplary. The scope of the invention should be determined by a reasonable interpretation of the appended claims, and all modifications within the equivalent scope of the invention are included within the scope of the invention.

Claims

1. A temperature control system, characterized in that, Includes a refrigerant circulation subsystem and a coolant circulation subsystem; The coolant circulation subsystem includes: Battery liquid cooling components are used to exchange heat between the coolant flowing through them and the energy storage battery. A drive unit for driving the coolant; The compressor drive module is located inside the electrical control box and is connected to the compressor. A liquid cooling plate is installed in conjunction with the compressor drive module to allow the coolant flowing through it to exchange heat with the compressor drive module. A flow regulating valve is used to regulate the flow rate of the coolant flowing through it; A temperature sensor for driving the liquid cooling plate is used to detect the surface temperature of the driving liquid cooling plate. A compressor drive module temperature sensor is used to detect the operating temperature of the compressor drive module; The refrigerant cycle subsystem includes: A compressor is used to compress refrigerant; A first heat exchanger is used to exchange heat between the refrigerant flowing through it and the air. The first four-way valve has a first port, a second port, a third port and a fourth port, wherein the third port is connected to the inlet end of the first heat exchanger and the fourth port is connected to the outlet end of the compressor. The second four-way valve has a first port, a second port, a third port and a fourth port, the first port being connected to the outlet end of the first heat exchanger and the second port being connected to the inlet end of the compressor; The first expansion valve is connected at both ends to the second interface and the fourth port, respectively. The second expansion valve is connected at one end to the outlet end of the compressor; The three-way valve has a first port, a second port and a third port, the first port being connected to the other end of the second expansion valve, and the second port being connected to the inlet end of the first heat exchanger; The temperature control system also includes: The refrigerant flowing out of the first port flows through the second heat exchanger to the third port, where it exchanges heat with the coolant flowing out of the outlet of the drive device. The refrigerant flowing out of the compressor outlet flows through the second expansion valve, the first port, the third port and the third heat exchanger to the inlet of the first heat exchanger, where it exchanges heat with the coolant flowing out of the drive device outlet in the third heat exchanger. Control unit, the control unit is configured to: When the temperature control system is operating in cooling mode, it controls the flow regulating valve to be fully open and the second expansion valve to be fully closed. If the temperature sensor of the driving liquid cooling plate detects that the surface temperature of the driving liquid cooling plate is below the set temperature of the driving liquid cooling plate, the second expansion valve is adjusted to make the surface temperature of the driving liquid cooling plate reach the set temperature of the driving liquid cooling plate, so as to replenish the temperature of the driving liquid cooling plate and prevent the coolant from condensing. The set temperature of the driving liquid cooling plate is determined based on the dew point temperature inside the electrical control box and is greater than the dew point temperature inside the electrical control box.

2. The temperature control system according to claim 1, characterized in that, The temperature control system also includes: Control unit, the control unit is configured to: When the temperature control system is operating in cooling mode, it controls the closing of the second port, allowing water to flow from the compressor's outlet. The refrigerant flows sequentially through the fourth port, the third port, the first heat exchanger, and the first port. The fourth port, the first expansion valve, the second interface, the first interface, the second heat exchanger, the third port, and the second port flow to the inlet of the compressor to form a first refrigerant main circuit; and The refrigerant flowing from the outlet of the compressor flows sequentially through the second expansion valve, the first port, and... The third port, the third heat exchanger, and the first heat exchanger together form a first refrigerant waste heat utilization branch.

3. The temperature control system according to claim 1, characterized in that, The control unit is also configured to: If the operating temperature of the compressor drive module is detected to be below the set temperature of the compressor drive module, the surface temperature of the drive liquid cooling plate is maintained at the set temperature of the drive liquid cooling plate, and the opening of the second expansion valve is reduced by adjusting the flow regulating valve and the second expansion valve; wherein, the set temperature of the compressor drive module is determined based on the maximum operating temperature of the compressor drive module and is less than the maximum operating temperature of the compressor drive module; When the operating temperature of the compressor drive module is detected to reach the set temperature of the compressor drive module or the second expansion valve is fully closed, the adjustment of the flow regulating valve and the second expansion valve is stopped.

4. The temperature control system according to claim 1, characterized in that, The control unit is also configured to: If the surface temperature of the driving liquid cooling plate is detected to be above the set temperature of the driving liquid cooling plate, the opening of the flow regulating valve and the second expansion valve shall be maintained. If the operating temperature of the compressor drive module is detected to be above the set temperature of the compressor drive module, the opening of the flow regulating valve and the second expansion valve shall be maintained.

5. The temperature control system according to claim 1, characterized in that, The temperature control system also includes: Control unit, the control unit is configured to: When the temperature control system operates in heating mode, the third port is closed, and the refrigerant flowing from the compressor outlet flows sequentially through the fourth port, the first port, the second heat exchanger, the third port, the fourth port, the first expansion valve, the second port, the third port, the first heat exchanger, the first port, and the second port to the compressor inlet, thus forming a second refrigerant main circuit; and The refrigerant flowing out from the outlet of the compressor flows sequentially through the second expansion valve, the first port, the second port and the first heat exchanger to form a second refrigerant waste heat utilization branch.

6. The temperature control system according to claim 5, characterized in that, The compressor drive module is located inside the electrical control box, and the coolant circulation subsystem also includes: A flow regulating valve is used to regulate the flow rate of the coolant flowing through it; The control unit is also configured to: When the temperature control system is running in heating mode, it controls the flow regulating valve to be fully open and controls the opening of the second expansion valve to be in a half-open and half-closed state to defrost the outer surface of the first heat exchanger.

7. The temperature control system according to claim 1, characterized in that, The refrigerant cycle subsystem also includes: Compressor suction temperature sensor, used to detect compressor suction temperature; Compressor suction pressure sensor, used to detect compressor suction pressure; The temperature control system further includes a control unit, which is configured to: The compressor evaporation temperature is determined based on the compressor suction pressure. Calculate the compressor suction superheat based on the compressor suction temperature and the compressor evaporation temperature; Calculate the difference in compressor suction superheat based on the compressor suction superheat and the target compressor suction superheat. Obtain the adjustment coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference; The opening degree of the first expansion valve is adjusted according to the adjustment coefficient, the current compressor suction superheat difference, and the historical compressor suction superheat difference.

8. The temperature control system according to claim 2, characterized in that, The coolant circulation subsystem also includes: A liquid outlet temperature sensor is installed at the outlet end of the battery liquid cooling plate assembly to detect the liquid outlet temperature of the energy storage battery. The control unit is also configured to: If the temperature of the liquid outlet of the energy storage battery is detected to be above the first target temperature of the liquid outlet of the energy storage battery, the temperature control system is controlled to operate the cooling mode. If the outlet temperature of the energy storage battery is detected to be below the outlet temperature of the second target energy storage battery, the temperature control system is controlled to stop operating the cooling mode, whereby the outlet temperature of the second target energy storage battery is lower than the outlet temperature of the first target energy storage battery.

9. The temperature control system according to claim 5, characterized in that, The coolant circulation subsystem also includes: A liquid outlet temperature sensor is located at the outlet end of the battery liquid cooling plate assembly and is used to detect the liquid outlet temperature of the energy storage battery. The control unit is also configured to: If the temperature of the liquid outlet of the energy storage battery is detected to be below the temperature of the third target energy storage battery, the temperature control system is controlled to operate the heating mode. If the detected temperature of the liquid outlet of the energy storage battery reaches or exceeds the second target temperature of the liquid outlet of the energy storage battery, the temperature control system is controlled to stop operating the heating mode, and the third target temperature of the liquid outlet of the energy storage battery is lower than the second target temperature of the liquid outlet of the energy storage battery.

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