Compressor module, control method of heating ventilation system, control device, electronic device and heating ventilation system

Abstract

The present disclosure provides a compressor module, a control method of a heating and ventilation system, a control device, an electronic device and a heating and ventilation system. The compressor module comprises a compressor, a gas-liquid separator, an adapter pipeline, a first expansion valve and a heat dissipation pipeline, the heat dissipation pipeline is used for dissipating heat of an electric control device of the heating and ventilation system; a first port of the adapter pipeline is used for connecting with a first heat exchange module of the heating and ventilation system, a second port is used for connecting with a second heat exchange module of the heating and ventilation system, a first branch pipeline is arranged between the first port and the second port, the first branch pipeline is connected with an inlet of the heat dissipation pipeline through the first expansion valve and a first branch pipeline; an outlet of the heat dissipation pipeline is connected with a suction port of the compressor through the gas-liquid separator; and / or, the outlet of the heat dissipation pipeline is connected with a spray enthalpy port of the compressor; an outlet of the first expansion valve is further connected with a discharge port of the compressor through a second branch pipeline and a second electromagnetic valve. The technical scheme of the present disclosure can improve the heat dissipation effect.

Description

Technical Field

[0001] This disclosure relates to the field of heating, ventilation and air conditioning (HVAC) technology, and in particular to a compressor module, a control method for an HVAC system, a control device, electronic equipment, and an HVAC system. Background Technology

[0002] HVAC systems include electrical control units, which consist of multiple electronic components. These units control electrical components such as compressors, fans, expansion valves, and solenoid valves. During the operation of the HVAC system, these electrical control units generate a significant amount of heat, requiring cooling measures.

[0003] In existing technologies, the heat dissipation methods for electronic control devices mainly include air cooling and refrigerant cooling. In air cooling, air ducts are installed on the heat dissipation pipes of the electronic control device, and air flows through the ducts to carry away heat. In refrigerant cooling, the electronic control device is in contact with the heat dissipation pipes, and liquid refrigerant flows through the heat dissipation pipes to carry away the heat from the electronic control device.

[0004] Existing refrigerant cooling methods have limited heat dissipation effects and cannot meet the requirements. Summary of the Invention

[0005] This disclosure provides a compressor module, a control method for a heating, ventilation and air conditioning (HVAC) system, a control device, an electronic device, and an HVAC system.

[0006] According to a first aspect of this disclosure, a compressor module is provided, including a compressor, a gas-liquid separator, a transfer pipeline, a first expansion valve, and a heat dissipation pipeline for dissipating heat from the electrical control device of a heating and ventilation system.

[0007] The first port of the transfer pipe is used to connect to the first heat exchange module of the HVAC system, and the second port of the transfer pipe is used to connect to the second heat exchange module of the HVAC system. A first branch pipe is provided between the first port and the second port of the transfer pipe. The first branch pipe is connected to the inlet of the first expansion valve, and the outlet of the first expansion valve is connected to the inlet of the heat dissipation pipe through the first branch pipe.

[0008] The outlet of the heat dissipation pipe is connected to the suction port of the compressor via a gas-liquid separator; and / or, the outlet of the heat dissipation pipe is connected to the enthalpy injection port of the compressor.

[0009] The outlet of the first expansion valve is also connected to one end of the second solenoid valve through the second branch pipe, and the other end of the second solenoid valve is connected to the exhaust port of the compressor.

[0010] In some embodiments, a first solenoid valve is provided between the outlet of the heat dissipation pipe and the inlet of the gas-liquid separator;

[0011] The first solenoid valve is configured to open under a first preset condition, so that the refrigerant flowing out of the heat dissipation pipe flows through the first solenoid valve and into the gas-liquid separator.

[0012] The first solenoid valve is also configured to shut off under a second preset condition, causing the refrigerant flowing out of the heat dissipation pipe outlet to flow to the compressor's enthalpy nozzle.

[0013] In some embodiments,

[0014] The second solenoid valve is configured to satisfy a preset time strategy when it is in the conducting state under the second preset condition, and the first expansion valve is configured to be closed when the second solenoid valve is in the conducting state, so that a portion of the refrigerant flowing out of the compressor's exhaust port flows through the second solenoid valve and the heat dissipation pipe and flows to the gas-liquid separator.

[0015] In some embodiments,

[0016] The first preset condition includes at least one of the following: the HVAC system is operating in cooling mode; the HVAC system is operating in heating mode and the ambient temperature is greater than or equal to the first preset temperature; and / or...

[0017] The second preset condition includes the HVAC system operating in heating mode and the ambient temperature being lower than the first preset temperature.

[0018] In some embodiments, the compressor module further includes a first temperature sensor for detecting the inlet temperature of the heat dissipation pipe and a second temperature sensor for detecting the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe, wherein the opening degree of the first expansion valve is determined based on the temperature difference between the second temperature sensor and the first temperature sensor.

[0019] In some embodiments, the first expansion valve can convert the refrigerant flowing through the first expansion valve into a two-phase refrigerant, which flows through a heat dissipation pipe to dissipate heat from the electronic control device.

[0020] In some embodiments, a subcooler is also included, the subcooler including a main pipeline disposed between a first port of the transfer pipeline and a first branch pipeline;

[0021] The subcooler also includes auxiliary piping, which includes at least a connecting section, through which the outlet of the heat dissipation pipe is connected to the gas-liquid separator; and / or, through the connecting section, the outlet of the heat dissipation pipe is connected to the enthalpy injection port of the compressor.

[0022] In some embodiments, the auxiliary piping also includes heat dissipation pipes.

[0023] According to a second aspect of this disclosure, a control method for a heating, ventilation, and air conditioning (HVAC) system is provided, the HVAC system including any compressor module of this disclosure, the control method comprising:

[0024] Determine the operating conditions of the HVAC system, including the first preset condition and the second preset condition;

[0025] The system is controlled by a first preset control strategy if the system meets the first preset condition; or, the system is controlled by a second preset control strategy if the system meets the second preset condition.

[0026] In some embodiments, a first preset control strategy is used to control the HVAC system, including:

[0027] The control opens the first expansion valve and turns on the first solenoid valve, so that at least a portion of the refrigerant in the transfer pipeline flows through the first expansion valve, the heat dissipation pipe and the first solenoid valve and flows to the gas-liquid separator.

[0028] In some embodiments, controlling the HVAC system using a first preset control strategy further includes:

[0029] Based on the auxiliary superheat and the target superheat, the opening of the first expansion valve is controlled so that the auxiliary superheat matches the target superheat. The auxiliary superheat is the difference between the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe and the inlet temperature of the heat dissipation pipe.

[0030] In some embodiments, controlling the opening degree of the first expansion valve based on the auxiliary superheat and the target superheat includes:

[0031] If the auxiliary circuit superheat is greater than the target superheat, increase the opening of the first expansion valve; or,

[0032] Based on the fact that the auxiliary circuit superheat equals the target superheat, maintain the opening of the first expansion valve; or,

[0033] If the superheat of the auxiliary circuit is less than the target superheat, reduce the opening of the first expansion valve.

[0034] In some embodiments, a second preset control strategy is used to control the HVAC system, including:

[0035] The first expansion valve is opened and the first solenoid valve is closed, so that at least a portion of the refrigerant in the transfer pipeline flows through the first expansion valve and the heat dissipation pipe and flows to the enthalpy injection port of the compressor.

[0036] In some embodiments, controlling the HVAC system using a second preset control strategy further includes:

[0037] If the temperature of the electronic control device is greater than the second preset temperature, the opening of the first expansion valve is increased so that the temperature of the electronic control device is less than or equal to the second preset temperature.

[0038] In some embodiments, controlling the HVAC system using a second preset control strategy further includes:

[0039] Based on the temperature of the electronic control device being less than or equal to the second preset temperature, and based on the auxiliary circuit superheat and the current target superheat, the opening of the first expansion valve is controlled so that the auxiliary circuit superheat matches the current target superheat. The auxiliary circuit superheat is the difference between the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe and the inlet temperature of the heat dissipation pipe.

[0040] In some embodiments, controlling the opening degree of the first expansion valve based on the auxiliary circuit superheat and the current target superheat includes:

[0041] If the auxiliary circuit superheat is greater than the current target superheat, increase the opening of the first expansion valve; or,

[0042] Based on the fact that the auxiliary circuit superheat equals the current target superheat, maintain the opening of the first expansion valve; or,

[0043] If the superheat of the auxiliary circuit is less than the current target superheat, reduce the opening of the first expansion valve.

[0044] In some embodiments, controlling the HVAC system using a second preset control strategy further includes:

[0045] The current target superheat is determined based on the exhaust superheat of the HVAC system and the initial target superheat.

[0046] In some embodiments, determining the current target superheat based on the exhaust superheat of the HVAC system and the initial target superheat includes:

[0047] If the exhaust superheat is less than a first preset value, the target superheat is increased based on the initial target superheat, and the increased target superheat is determined as the current target superheat; or...

[0048] If the exhaust superheat meets the preset range, the initial target superheat is determined as the current target superheat; or...

[0049] Based on the fact that the exhaust superheat is greater than the second preset value, the target superheat is reduced from the initial target superheat, and the reduced target superheat is determined as the current target superheat.

[0050] The second preset value is greater than the first preset value.

[0051] In some embodiments, before controlling the opening of the first expansion valve and the closing of the first solenoid valve, the second preset control strategy is used to control the HVAC system, which further includes:

[0052] The first expansion valve is shut off, and both the first and second solenoid valves are turned on, so that a portion of the refrigerant flowing out of the compressor's exhaust port flows through the second solenoid valve, the heat dissipation pipe, and the first solenoid valve and flows to the inlet of the gas-liquid separator.

[0053] In some embodiments,

[0054] The control of the first expansion valve being closed and the first and second solenoid valves being both open satisfies a preset time strategy.

[0055] In some embodiments,

[0056] The preset time strategy includes maintaining the system for a first preset duration if the exhaust superheat of the HVAC system exceeds a first preset value; or,

[0057] The preset time strategy includes a duration longer than the second preset duration.

[0058] In some embodiments,

[0059] The first preset duration is greater than or equal to 5 minutes; or, the second preset duration is in the range of 10 minutes to 30 minutes.

[0060] In some embodiments, determining the operating conditions of the HVAC system includes:

[0061] Obtain the operating mode and ambient temperature of the HVAC system;

[0062] The system is determined to meet the first preset condition based on the operating mode being cooling mode; or, the system is determined to meet the first preset condition based on the operating mode being heating mode and the ambient temperature being greater than or equal to the first preset temperature; or, the system is determined to meet the second preset condition based on the operating mode being heating mode and the ambient temperature being less than the first preset temperature.

[0063] According to a third aspect of this disclosure, a control device for a heating, ventilation, and air conditioning (HVAC) system is provided, the HVAC system including the compressor module of any of the present disclosure, the control device being configured to implement the control method of any of the present disclosure.

[0064] According to a fourth aspect of this disclosure, an electronic device is provided, comprising:

[0065] At least one processor; and

[0066] A memory that is communicatively connected to at least one processor; wherein,

[0067] The memory stores instructions that can be executed by at least one processor to enable the at least one processor to perform the control method of any one of claims 9-23.

[0068] According to a fifth aspect of this disclosure, a heating, ventilation, and air conditioning system is provided, including a compressor module of any one of the present disclosures, and also including a control device or electronic device of the present disclosure.

[0069] In some embodiments, it also includes:

[0070] A first heat exchange module includes at least one first heat exchange module. When the first heat exchange module includes multiple first heat exchange modules, the multiple first heat exchange modules are connected in parallel. The first port of the first heat exchange module is connected to a four-way valve in the compressor module through a first pipeline, and the second port of the first heat exchange module is connected to the first port of the transfer pipeline; and / or...

[0071] The second heat exchange module includes at least one second heat exchange module. When the second heat exchange module includes multiple second heat exchange modules, the multiple second heat exchange modules are connected in parallel. The second port of the transfer pipeline is connected to the first port of the second heat exchange module through a third pipeline. The second port of the second heat exchange module is connected to the four-way valve in the compressor module through a second pipeline.

[0072] The technical solution disclosed herein connects a heat dissipation pipe for cooling the electronic control device to a first expansion valve. A portion of the liquid refrigerant flowing from the transfer pipe through the first branch pipe becomes a two-phase refrigerant (i.e., a mixture of liquid and gaseous refrigerant) after passing through the first expansion valve. The temperature of the two-phase refrigerant is lower than that of the liquid refrigerant. When the two-phase refrigerant flows through the heat dissipation pipe, the heat exchange temperature difference of the electronic control device is the difference between the temperature of the two-phase refrigerant and the temperature of the electronic control device. Since the temperature of the two-phase refrigerant is much lower than that of the liquid refrigerant, the heat exchange temperature difference between the electronic control device and the two-phase refrigerant is greater in this disclosure compared to using liquid refrigerant for heat dissipation. When the two-phase refrigerant flows through the heat dissipation pipe, it can carry away more heat, thus better cooling the electronic control device and achieving a better heat dissipation effect.

[0073] The technical solution disclosed herein uses a two-phase refrigerant to dissipate heat from the electronic control device, resulting in a larger heat exchange temperature difference and improved heat exchange capacity. While maintaining the same heat dissipation capacity, the heat dissipation area can be reduced, thereby reducing the size of the heat dissipation pipes and lowering costs. While maintaining the same heat dissipation area, the heat dissipation capacity can be improved, achieving a better heat dissipation effect.

[0074] In addition, the outlet of the first expansion valve is also connected to the exhaust port of the compressor through the second branch pipe and the second solenoid valve. Thus, when the ambient temperature is low and the HVAC system may fail to start, the second solenoid valve can be opened to allow a portion of the gaseous refrigerant with a higher temperature flowing out of the compressor outlet to flow through the second solenoid valve and the heat dissipation pipe, heating the electronic control device 16 and raising its temperature. This facilitates the start-up of the electronic control device and prevents the HVAC system from failing to start at low temperatures.

[0075] It should be understood that the description in this section is not intended to identify key or essential features of the embodiments of this disclosure, nor is it intended to limit the scope of this disclosure. Other features of this disclosure will become readily apparent from the following description. Attached Figure Description

[0076] The accompanying drawings are provided to better understand this solution and do not constitute a limitation of this disclosure. Wherein:

[0077] Figure 1 This is a schematic diagram of the connection of the compressor module in one embodiment of the present disclosure;

[0078] Figure 2 This is a connection diagram of the compressor module in another embodiment of the present disclosure;

[0079] Figure 3 This is a pressure-enthalpy diagram of the HVAC system in cooling mode;

[0080] Figure 4 This is a connection diagram of the compressor module in yet another embodiment of the present disclosure;

[0081] Figure 5 This is a schematic diagram of the connection of a heating, ventilation, and air conditioning system according to one embodiment of the present disclosure;

[0082] Figure 6 This is a schematic diagram of the connection of the HVAC system in another embodiment of this disclosure;

[0083] Figure 7 This is a schematic diagram of a control method for a heating, ventilation, and air conditioning system according to an embodiment of the present disclosure;

[0084] Figure 8 This is a schematic diagram of the connection of the HVAC system in heating mode according to an embodiment of the present disclosure;

[0085] Figure 9 This is a pressure-enthalpy diagram of the HVAC system in heating mode;

[0086] Figure 10 This is a flowchart of a control method for a heating, ventilation, and air conditioning system according to an embodiment of this disclosure;

[0087] Figure 11 This is an exemplary structural diagram of an electronic device provided in an embodiment of this disclosure.

[0088] Explanation of reference numerals in the attached figures:

[0089] 10. Compressor module; 11. Compressor; 12. Gas-liquid separator; 13. Subcooler; 131. Main pipeline of subcooler; 132. Auxiliary pipeline of subcooler; 15. Heat dissipation pipeline; 16. Electrical control device; 17. Four-way valve; 20. First heat exchange module; 21. First heat exchange module; 30. Second heat exchange module; 31. Second heat exchange module; 41. First pipeline; 42. Transfer pipeline; 43. Third pipeline; 44. Second pipeline; 45. Fifth pipeline; 46. Sixth pipeline; 47. Seventh pipeline. Detailed Implementation

[0090] The exemplary embodiments of this disclosure are described below with reference to the accompanying drawings, including various details of the embodiments to aid understanding, and should be considered merely exemplary. Therefore, those skilled in the art will recognize that various changes and modifications can be made to the embodiments described herein without departing from the scope and spirit of this disclosure. Similarly, for clarity and brevity, descriptions of well-known functions and structures are omitted in the following description.

[0091] Figure 1 This is a schematic diagram of the connection of the compressor module in one embodiment of the present disclosure. Figure 2 This is a connection diagram of the compressor module in another embodiment of this disclosure. Figure 1 and Figure 2 As shown, the compressor module 10 includes a compressor 11, a gas-liquid separator 12, a transfer pipe 42, a first expansion valve E1, and a heat dissipation pipe 15. The heat dissipation pipe 15 is used to dissipate heat from the electrical control device 16 of the HVAC system.

[0092] The transfer pipe 42 has a first port and a second port. The first port of the transfer pipe 42 is used to connect to the first heat exchange module 20 of the HVAC system, and the second port of the transfer pipe 42 is used to connect to the second heat exchange module 30 of the HVAC system.

[0093] like Figure 1 and Figure 2 As shown, the compressor module 10 may also include a four-way valve 17, which has ports A, B, C, and D. The HVAC system includes a first heat exchange module 20 and a second heat exchange module 30. The second heat exchange module 30 may be located indoors.

[0094] The outlet of compressor 11 is connected to port A, and port B is used to connect to the first port of the first heat exchange module 20 via the first pipe 41. Port C is used to connect to the second port of the second heat exchange module 30 via the second pipe 44. Port D is connected to the suction port of compressor 11 via gas-liquid separator 12. The first port of transfer pipe 42 is connected to the second port of the first heat exchange module 20, and the second port of transfer pipe 42 is connected to the first port of the second heat exchange module 30. By changing the state of the four-way valve 17, the flow direction of refrigerant between the first heat exchange module 20 and the second heat exchange module 30 can be controlled. For example, in cooling mode, refrigerant flows from the first heat exchange module 20 to the second heat exchange module 30 via transfer pipe 42; in heating mode, refrigerant flows from the second heat exchange module 30 to the first heat exchange module 20 via transfer pipe 42.

[0095] A first branch pipe 61 is provided between the first and second ports of the transfer pipe 42. For example, a first tee connector 71 can be connected to the transfer pipe 42. The first and second ports of the first tee connector 71 can be connected to the transfer pipe 42 respectively, and the third port of the first tee connector 71 can be connected to the first branch pipe 61. The first branch pipe 61 is connected to the inlet of the first expansion valve E1, and the outlet of the first expansion valve E1 is connected to the inlet of the heat dissipation pipe 15 through the first branch pipe 62.

[0096] The outlet of the heat dissipation pipe 15 can be connected to the inlet of the compressor 11 through the gas-liquid separator 12; and / or, the outlet of the heat dissipation pipe 15 can be connected to the enthalpy injection port of the compressor 11.

[0097] In one embodiment, the outlet of the heat dissipation pipe 15 can be connected to the first port of the second tee connector 72, the second port of the second tee connector 72 can be connected to the inlet of the compressor 11 through the gas-liquid separator 12, and the third port of the second tee connector 72 can be connected to the enthalpy injection port of the compressor 11.

[0098] For example, under a first preset condition, the outlet of the heat dissipation pipe 15 is connected to the inlet of the compressor 11 through the gas-liquid separator 12, so that the refrigerant flowing out of the outlet of the heat dissipation pipe 15 flows to the gas-liquid separator 12 and then enters the inlet of the compressor 11. Under a second preset condition, the outlet of the heat dissipation pipe 15 is connected to the enthalpy injection port of the compressor 11, so that the refrigerant flowing out of the outlet of the heat dissipation pipe 15 flows to the enthalpy injection port of the compressor 11.

[0099] The first expansion valve E1 can be an electronic expansion valve. The first expansion valve E1 has an installation direction, and its inlet and outlet can be determined with reference to this direction. The inlet of the first expansion valve E1 can be the front end of its installation direction, and the outlet can be the rear end. The first expansion valve can convert the refrigerant flowing through it into a two-phase refrigerant, which flows through the heat dissipation pipe to cool the electronic control device.

[0100] The heat dissipation pipe 15 is used to dissipate heat from the electronic control device 16. For better heat dissipation, the heat dissipation pipe 15 can be serpentine or spiral-shaped. The heat dissipation pipe 15 maintains good contact with the electronic control device 16. Exemplarily, the electronic control device 16 may include an electronic control box and a control module, with the control module located inside the electronic control box. The heat dissipation pipe 15 can contact the electronic control box to dissipate heat from the electronic control device.

[0101] Figure 3This is a pressure-enthalpy diagram of an HVAC system in cooling mode. In related technologies, electrical control devices typically use liquid refrigerant for heat dissipation; that is, the heat dissipation pipes used to cool the electrical control devices are connected to the liquid refrigerant piping. Figure 3 The diagram shows location A where the electronic control device uses liquid refrigerant for heat dissipation. The temperature of the liquid refrigerant is a first temperature, approximately 40°C. The heat exchange temperature difference of the electronic control device is the difference between the first temperature and the temperature of the electronic control device itself.

[0102] It should be noted that the electronic control device includes multiple electronic components, which can form different control modules. For example, the electronic control device may include a compressor control module for controlling the operation of the compressor, a fan control module for controlling the operation of the fan, etc. The temperature of the electronic control device can be the maximum value among the temperatures of the multiple control modules, or the temperature of the electronic control device can be the average value of the temperatures of the multiple control modules.

[0103] The technical solution disclosed herein connects the heat dissipation pipe 15, which is used to dissipate heat from the electronic control device 16, after the first expansion valve E1. A portion of the liquid refrigerant flowing out of the transfer pipe 42 through the first branch pipe 61 becomes a two-phase refrigerant (i.e., a mixture of liquid refrigerant and gaseous refrigerant) after passing through the first expansion valve E1. The temperature of the two-phase refrigerant is lower than that of the liquid refrigerant. Figure 3 The location B of the electronic control device 16 in the cooling mode, as shown in this embodiment, is where two-phase refrigerant heat dissipation is used. Figure 3 It can be seen that the temperature at position B is the second temperature, which is lower than the first temperature, for example, the second temperature is approximately 10°C. When the two-phase refrigerant flows through the heat dissipation pipe, the heat exchange temperature difference of the electronic control device 16 is the difference between the second temperature and the temperature of the electronic control device 16. Since the temperature of the two-phase refrigerant is much lower than the temperature of the liquid refrigerant (the second temperature is lower than the first temperature), the heat exchange temperature difference of the electronic control device 16 in this disclosure is larger than that in related technologies. When the two-phase refrigerant flows through the heat dissipation pipe, it can carry away more heat, and can better dissipate heat from the electronic control device 16, achieving a better heat dissipation effect.

[0104] The technical solution disclosed herein uses a two-phase refrigerant to dissipate heat from the electronic control device 16, resulting in a larger heat exchange temperature difference and improved heat exchange capacity. While maintaining the same heat dissipation capacity, the heat dissipation area can be reduced, thereby reducing the size of the heat dissipation pipe 15 and lowering costs. While maintaining the same heat dissipation area, the heat dissipation capacity can be improved, achieving a better heat dissipation effect.

[0105] In one embodiment, such as Figure 1 and Figure 2As shown, a first solenoid valve V1 is installed between the outlet of the heat dissipation pipe 15 and the inlet of the gas-liquid separator 12. The first solenoid valve V1 can be a two-way valve. The first solenoid valve V1 can be installed between the second three-way connector 72 and the inlet of the gas-liquid separator 12.

[0106] The first solenoid valve V1 is configured to open under a first preset condition, so that the refrigerant flowing out of the outlet of the heat dissipation pipe 15 flows through the first solenoid valve V1 and into the gas-liquid separator 12. After passing through the gas-liquid separator 12, the liquid refrigerant remains in the gas-liquid separator 12, while the gaseous refrigerant flows from the outlet of the gas-liquid separator 12 to the inlet of the compressor 11.

[0107] The first solenoid valve V1 is also configured to close under a second preset condition, causing the refrigerant flowing from the outlet of the heat dissipation pipe 15 to flow to the enthalpy injection port of the compressor 11. Thus, the heat dissipation pipe 15 is located in the enthalpy injection circuit. The enthalpy injection circuit includes: first branch pipe 61 → first expansion valve E1 → heat dissipation pipe 15 → enthalpy injection port of the compressor 11.

[0108] By setting the first solenoid valve V1 and controlling its opening and closing, the compressor module 10 can adapt to either the first preset condition or the second preset condition. Thus, regardless of whether it is the first preset condition or the second preset condition, two-phase refrigerant can be used to dissipate heat from the electronic control device 16.

[0109] For example, the first preset condition includes at least one of the following: the HVAC system is operating in cooling mode; the HVAC system is operating in heating mode and the ambient temperature is greater than or equal to the first preset temperature. The first preset temperature may be the minimum temperature at which the electronic control device 16 can operate, for example, the first preset temperature may be less than or equal to -20°C.

[0110] For example, the second preset condition includes the HVAC system operating in heating mode and the ambient temperature being lower than the first preset temperature. Under the second preset condition, the ambient temperature is very low, for example, the first preset temperature is -30°C. When the ambient temperature is lower than -30°C, in such an environment, the first solenoid valve V1 is shut off, causing the refrigerant flowing out of the outlet of the heat dissipation pipe 15 to flow to the enthalpy injection port of the compressor 11. The circuit containing the heat dissipation pipe 15 adopts an enthalpy injection circuit, which can raise the evaporation temperature of the heat dissipation pipe 15, prevent the evaporation temperature from falling below the ambient temperature, prevent the components in the electronic control device 16 from being cooled below -30°C, and ensure that the components are within the allowable operating range.

[0111] like Figure 1 and Figure 2 As shown, Figure 1 and Figure 2As shown, the outlet of the first expansion valve E1 is also connected to one end of the second solenoid valve V2 through the second branch pipe 63. The other end of the second solenoid valve V2 can be connected to the exhaust port of the compressor 11. Thus, the outlet of the compressor 11 is connected to the inlet of the heat dissipation pipe 15 through the second solenoid valve V2.

[0112] The second solenoid valve V2 can be a two-way valve. The second solenoid valve V2 can be configured to open under a second preset condition, and the opening state of the second solenoid valve V2 satisfies a preset time strategy. The first expansion valve E1 is configured to close when the second solenoid valve V2 is open, so that a portion of the refrigerant flowing out of the compressor 11 flows through the second solenoid valve V2 and the heat dissipation pipe 15 and flows to the gas-liquid separator 12.

[0113] Under the second preset condition, the ambient temperature is lower than the first preset temperature, which may prevent the HVAC system from starting. In heating mode, the gaseous refrigerant discharged from the compressor 11 has a higher temperature. By setting the second solenoid valve V2 to be in the on state under the second preset condition to meet the preset time strategy and closing the first expansion valve E1, a portion of the higher-temperature gaseous refrigerant flowing from the compressor 11 outlet can flow through the second solenoid valve V2 and the heat dissipation pipe 15. When the higher-temperature gaseous refrigerant flows through the heat dissipation pipe 15, it exchanges heat with the lower-temperature electronic control device 16, heating the electronic control device 16 and raising its temperature. This facilitates the starting of the electronic control device 16, thereby better starting the HVAC system and preventing the HVAC system from failing to start at low temperatures.

[0114] For example, when the second solenoid valve V2 is open, the first solenoid valve V1 is open so that the refrigerant flowing out of the heat dissipation pipe 15 can flow through the first solenoid valve V1 to the gas-liquid separator 12.

[0115] For example, the compressor module 10 further includes a first temperature sensor T6A and a second temperature sensor T6B. The first temperature sensor T6A is used to detect the inlet temperature of the heat dissipation pipe 15, and the second temperature sensor T6B is used to detect the refrigerant temperature after the outlet of the heat dissipation pipe 15. The opening degree of the first expansion valve E1 is determined based on the temperature difference between the second temperature sensor T6B and the first temperature sensor T6A, or in other words, the opening degree of the first expansion valve E1 is determined based on the temperature difference between the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe 15 and the inlet temperature of the heat dissipation pipe 15.

[0116] The temperature difference between the refrigerant temperature at the preset position after the outlet of the heat dissipation pipe 15 and the inlet temperature of the heat dissipation pipe 15 can be called the auxiliary superheat. The opening degree of the first expansion valve E1 is determined based on the auxiliary superheat, which helps to match the auxiliary superheat with the target superheat and improve the energy efficiency of the HVAC system.

[0117] like Figure 1 and Figure 2 As shown, the compressor module 10 may further include a subcooler 13, which includes a main pipeline 131 and an auxiliary pipeline 132. The main pipeline 131 is located between the first port of the transfer pipeline 42 and the first branch pipeline 61. The auxiliary pipeline 132 includes at least a connecting section 1321, through which the outlet of the heat dissipation pipe 15 is connected to the gas-liquid separator 12; and / or, the outlet of the heat dissipation pipe 15 is connected to the enthalpy injection port of the compressor 11 through the connecting section 1321. For example, the connecting section 1321 may be connected between the second tee connector 72 and the outlet of the heat dissipation pipe 15. A second temperature sensor T6B may be located at the outlet of the connecting section 1321 to detect the refrigerant temperature at the outlet of the auxiliary pipeline 132.

[0118] It should be noted that when the compressor module 10 is not equipped with a subcooler 13, the preset position after the outlet of the heat dissipation pipe 15 can be the outlet position of the heat dissipation pipe 15; when the subcooler 13 is equipped, the preset position after the outlet of the heat dissipation pipe 15 can be the outlet position of the auxiliary pipe 132 of the subcooler 13.

[0119] In one embodiment, such as Figure 1 and Figure 2 As shown, the heat dissipation pipe 15 is independent of the auxiliary pipe 132, and can be located between the inlet of the auxiliary pipe 132 and the first expansion valve E1. The housing of the electronic control device 16 can contact the surface of the heat dissipation pipe 15 through a heat-conducting medium, so that the heat dissipation pipe 15 can dissipate heat from the electronic control device 16. Alternatively, the electronic control device 16 can be provided with a cavity, and the electrical components can be installed in the cavity. The heat dissipation pipe 15 can be located in the cavity to dissipate heat from the electrical components inside the cavity.

[0120] Figure 4 This is a connection diagram of the compressor module in another embodiment of the present disclosure. Figure 4 In this embodiment, the auxiliary conduit 132 includes a heat dissipation conduit 15. For example, a portion of the auxiliary conduit 132 may be used as the heat dissipation conduit 15, or the auxiliary conduit 132 may also serve as the heat dissipation conduit 15. Exemplarily, the auxiliary conduit 132 may be installed inside the packaging of the electronic control device 16, or the heating surface in the electronic control device 16 may be brought into contact with the auxiliary conduit 132 to dissipate heat from the electronic control device 16.

[0121] Figure 5 This is a schematic diagram of the connection of a heating, ventilation, and air conditioning system according to one embodiment of the present disclosure. Figure 6 This is a schematic diagram of the connection of the HVAC system according to another embodiment of this disclosure. Figure 5 and Figure 6As shown, the HVAC system includes the compressor module 10 in this embodiment, and also includes a first heat exchange module 20 and a second heat exchange module 30. The first heat exchange module 20 includes at least one first heat exchange module 21. The first heat exchange module 21 may include a first heat exchanger and a second expansion valve connected in series. When the first heat exchange module 20 includes multiple first heat exchange modules 21, the multiple first heat exchange modules 21 are connected in parallel. The first port of the first heat exchange module 20 is connected to a four-way valve 17 in the compressor module 10 via a first pipe 41. For example, the first port of the first heat exchange module 20 is connected to port B of the four-way valve 17 in the compressor module 10 via the first pipe 41. The second port of the first heat exchange module 20 is connected to a transfer pipe 42.

[0122] exist Figure 5 In this embodiment, the first heat exchange module 20 may include a first heat exchange module 21, which may be part of the compressor module 10; that is, the compressor module 10 includes the first heat exchange module 21. The first heat exchange module 21 includes a first heat exchanger and a second expansion valve. The second expansion valve is connected in series with the first heat exchanger.

[0123] exist Figure 6 In this embodiment, the first heat exchange module 20 includes a plurality of first heat exchange modules 21 connected in parallel. The first heat exchange module 20 is located outdoors and is independent of the compressor module 10.

[0124] like Figures 1-6 As shown, the compressor module 10 may include a second pipe 44, one end of which is connected to port C of the four-way valve 17, and the other end of which can be connected to a second connector 52. The second connector 52 can be connected to the second port of the second heat exchange module 30 via a fifth pipe 45. The second port of the transfer pipe 42 can be connected to a first connector 51. The first connector 51 can be connected to the first port of the second heat exchange module 30 via a third pipe 43.

[0125] When the first heat exchange module 20 is located outdoors, one end of the first pipe 41 can be connected to the fourth connector 54. The fourth connector 54 can be connected to the first port of the first heat exchange module 20 via the seventh pipe 47. The first port of the transfer pipe 42 can be connected to the third connector 53, and the third connector 53 can be connected to the second port of the first heat exchange module 20 via the sixth pipe 46.

[0126] like Figure 5 and Figure 6As shown, the second heat exchange module 30 includes at least one second heat exchange module 31, which may include a second heat exchanger and a third expansion valve connected in series. When the second heat exchange module 30 includes multiple second heat exchange modules 31, the multiple second heat exchange modules 31 are connected in parallel. The first connector 51 is connected to the first port of the second heat exchange module 30 through the third pipe 43. The second connector 52 can be connected to the second port of the second heat exchange module 30 through the fifth pipe 45. Thus, the second port of the second heat exchange module 30 is connected to the port C of the four-way valve 17 in the compressor module 10 through the fifth pipe 45, the second connector 52, and the second pipe 44.

[0127] exist Figure 1 , Figure 2 , Figures 4-6 In this embodiment, the four-way valve 17 is in cooling mode, meaning that in the four-way valve 17, port A is connected to port B, and port C is connected to port D. In heating mode, in the four-way valve 17, port A is connected to port C, and port B is connected to port D.

[0128] Figure 7 This is a schematic diagram of a control method for a heating, ventilation, and air conditioning (HVAC) system according to an embodiment of this disclosure. The HVAC system includes the compressor module 10 from any embodiment of this disclosure. Figure 7 As shown, the control method for the HVAC system may include steps S10 to S20.

[0129] In step S10, the operating conditions of the HVAC system are determined, including a first preset condition and a second preset condition.

[0130] In step S20, the HVAC system is controlled by a first preset control strategy based on the first preset condition; or, the HVAC system is controlled by a second preset control strategy based on the second preset condition.

[0131] The control method of this embodiment employs step S21, i.e., a first preset control strategy, to control the HVAC system under a first preset condition; and step S22, i.e., a second preset control strategy, to control the HVAC system under a second preset condition. Therefore, by employing different preset control strategies to control the HVAC system under different preset conditions, the optimal efficiency of the HVAC system can be achieved.

[0132] In one embodiment, determining the operating conditions of the HVAC system includes: acquiring the operating mode and ambient temperature of the HVAC system; determining that the HVAC system meets a first preset condition based on the operating mode being a cooling mode; or, determining that the HVAC system meets the first preset condition based on the operating mode being a heating mode and the ambient temperature being greater than or equal to the first preset temperature; or, determining that the HVAC system meets a second preset condition based on the operating mode being a heating mode and the ambient temperature being less than the first preset temperature.

[0133] The ambient temperature refers to the outdoor ambient temperature. The HVAC system may include a third temperature sensor for detecting the outdoor ambient temperature. When the operating mode is heating mode and the temperature detected by the third temperature sensor is greater than or equal to a first preset temperature, the HVAC system is determined to meet the first preset condition; when the operating mode is heating mode and the temperature detected by the third temperature sensor is less than the first preset temperature, the HVAC system is determined to meet the second preset condition.

[0134] In one embodiment, a first solenoid valve V1 is provided between the outlet of the heat dissipation pipe 15 and the inlet of the gas-liquid separator 12. The HVAC system is controlled by a first preset control strategy, including: controlling the opening of the first expansion valve E1 and the conduction of the first solenoid valve V1, so that at least a portion of the refrigerant in the transfer pipe 42 flows through the first expansion valve E1, the heat dissipation pipe 15 and the first solenoid valve V1 and flows to the gas-liquid separator 12.

[0135] Figure 8 This is a schematic diagram of the connection of the heating and ventilation system in heating mode according to one embodiment of the present disclosure. Figure 5 and Figure 6 In the middle, the HVAC system operates in cooling mode. In heating mode, such as Figure 8 As shown, port A of the four-way valve 17 is connected to port C, and port B is connected to port D.

[0136] The first preset condition includes the HVAC system operating in cooling mode, or the HVAC system operating in heating mode and the ambient temperature being greater than or equal to the first preset temperature. Therefore, under the first preset condition, the ambient temperature is greater than or equal to the first preset temperature. The first preset temperature can be the minimum temperature at which the electronic control device 16 can operate, thus, under the first preset condition, the ambient temperature is greater than or equal to the minimum temperature at which the electronic control device 16 can operate.

[0137] When the HVAC system is controlled using the first preset control strategy, at least a portion of the refrigerant in the transfer pipe 42 flows through the first expansion valve E1 and becomes a gas-liquid two-phase refrigerant. The temperature of the gas-liquid two-phase refrigerant is lower than that of the liquid refrigerant, and the heat exchange temperature difference between the gas-liquid two-phase refrigerant and the electronic control device 16 is greater than that between the liquid refrigerant and the electronic control device 16. Therefore, when the gas-liquid two-phase refrigerant flows through the heat dissipation pipe 15, it can carry away more heat from the electronic control device 16, thus better dissipating heat from the electronic control device 16 and achieving a better heat dissipation effect.

[0138] In one embodiment, controlling the HVAC system using a first preset control strategy further includes: controlling the opening degree of the first expansion valve E1 based on the auxiliary circuit superheat and the target superheat, so that the auxiliary circuit superheat matches the target superheat. The auxiliary circuit superheat is the difference between the refrigerant temperature at a preset location after the outlet of the heat dissipation pipe 15 and the inlet temperature of the heat dissipation pipe 15.

[0139] The target superheat can be the target temperature difference between the refrigerant temperature at a preset location after the outlet of the heat dissipation pipe 15 in the HVAC system and the refrigerant temperature at the inlet of the heat dissipation pipe 15. When the auxiliary circuit superheat matches the target superheat, it is beneficial to improve the efficiency and performance of the HVAC system. In this embodiment of the present disclosure, the opening degree of the first expansion valve E1 is controlled based on the auxiliary circuit superheat and the target superheat, so that the auxiliary circuit superheat matches the target superheat, thereby improving the efficiency and performance of the HVAC system.

[0140] The target superheat value can be set by those skilled in the art based on conventional requirements. Before the HVAC system is put into operation, a target superheat value can be set for the HVAC system based on experience. Under the first preset conditions, the target superheat value can meet the requirements of the HVAC system. Therefore, this setting value is used as the target superheat value during the operation of the HVAC system.

[0141] like Figure 5 , Figure 6 , Figure 8 As shown, during the operation of the HVAC system, the inlet temperature of the heat dissipation pipe 15 can be detected by the first temperature sensor T6A, and the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe 15 can be detected by the second temperature sensor T6B. In this way, the auxiliary circuit superheat can be obtained in real time. Based on the auxiliary circuit superheat and the target superheat, the opening degree of the first expansion valve E1 can be controlled.

[0142] It should be noted that when the first expansion valve E1 is opened, the opening degree of the first expansion valve E1 is usually a preset opening degree, which can be about 50% of the full opening degree of the first expansion valve E1. After the first expansion valve E1 is opened, the opening degree of the first expansion valve E1 can be controlled based on the auxiliary circuit superheat and the target superheat, so that the auxiliary circuit superheat matches the target superheat.

[0143] When controlling the HVAC system using the first preset control strategy, the opening of the first expansion valve E1 is controlled based on the auxiliary circuit superheat and the target superheat, including: increasing the opening of the first expansion valve E1 when the auxiliary circuit superheat is greater than the target superheat; or maintaining the opening of the first expansion valve E1 when the auxiliary circuit superheat is equal to the target superheat; or decreasing the opening of the first expansion valve E1 when the auxiliary circuit superheat is less than the target superheat.

[0144] When the superheat of the auxiliary circuit is greater than the target superheat, the opening of the first expansion valve E1 can be increased, allowing more refrigerant to flow through the first expansion valve E1, thereby allowing more gas-liquid two-phase refrigerant to flow through the heat dissipation pipe 15, improving the cooling effect of the two-phase refrigerant, and thus reducing the refrigerant temperature at the preset position after the outlet of the heat dissipation pipe 15, reducing the superheat of the auxiliary circuit, and making the superheat of the auxiliary circuit match the target superheat.

[0145] When the auxiliary superheat is less than the target superheat, the opening of the first expansion valve E1 can be reduced, so that less refrigerant flows through the first expansion valve E1, and thus less gas-liquid two-phase refrigerant flows through the heat dissipation pipe 15, reducing the cooling effect of the two-phase refrigerant. This can increase the refrigerant temperature at the preset position after the outlet of the heat dissipation pipe 15, increase the auxiliary superheat, and make the auxiliary superheat match the target superheat.

[0146] When the auxiliary circuit superheat equals the target superheat, the opening of the first expansion valve E1 is maintained. It should be noted that the auxiliary circuit superheat equaling the target superheat can be understood as the difference between the auxiliary circuit superheat and the target superheat being within a preset range (e.g., an error range), or the auxiliary circuit superheat matching the target superheat.

[0147] In one embodiment, the outlet of compressor 11 is connected to the inlet of heat dissipation pipe 15 via a second solenoid valve V2. Therefore, when controlling the HVAC system using the first preset control strategy, while controlling the opening of the first expansion valve E1 and the conduction of the first solenoid valve V1, the second solenoid valve V2 is simultaneously closed, cutting off the connection between the outlet of compressor 11 and the inlet of heat dissipation pipe 15, thus preventing refrigerant from the outlet of compressor 11 from flowing into heat dissipation pipe 15.

[0148] In one embodiment, the second preset condition includes the HVAC system operating in heating mode and the ambient temperature being lower than the first preset temperature. Under the second preset condition, the ambient temperature is very low. For example, the first preset temperature can be the minimum temperature at which the electronic control device 16 can operate; in this case, the ambient temperature under the second preset condition is lower than the minimum temperature at which the electronic control device 16 can operate.

[0149] Under the second preset conditions, the second preset control strategy is used to control the HVAC system, including step S221. In step S221, the first expansion valve E1 is opened and the first solenoid valve V1 is closed, so that at least a portion of the refrigerant in the transfer pipe 42 flows through the first expansion valve E1, the heat dissipation pipe 15 and flows to the enthalpy port of the compressor 11.

[0150] It should be noted that when the first expansion valve E1 is opened, the opening degree of the first expansion valve E1 is usually the preset opening degree, which can be about 50% of the full opening degree of the first expansion valve E1.

[0151] Under the second preset condition, the ambient temperature is very low, for example, the first preset temperature is -30℃. The ambient temperature is less than -30℃. Under such an ambient temperature, when using the second preset control strategy to control the HVAC system, refer to... Figure 8 The heat dissipation pipe 15 is located in the enthalpy injection circuit. The gas-liquid two-phase refrigerant in the enthalpy injection circuit can absorb the heat from the electronic control device 16, thereby cooling the electronic control device 16. The pressure of the refrigerant in the enthalpy injection circuit is greater than the pressure at the compressor suction port and less than the pressure at the compressor discharge port.

[0152] Understandably, the components in the electronic control device 16 typically have an allowable operating range, and will malfunction when their temperature exceeds this range. Under the second preset condition, the ambient temperature is very low; for example, the first preset temperature is -30°C, and the ambient temperature is below -30°C. At such an ambient temperature, when the second preset control strategy is used to control the HVAC system, the first solenoid valve V1 is shut off, causing the refrigerant flowing from the heat dissipation pipe 15 to flow to the enthalpy injection port of the compressor 11. The circuit containing the heat dissipation pipe 15 uses an enthalpy injection circuit, which can raise the evaporation temperature of the heat dissipation pipe 15, preventing it from falling below the ambient temperature and preventing the components in the electronic control device 16 from being cooled below -30°C, thus ensuring that the components remain within their allowable operating range.

[0153] After the refrigerant in the enthalpy-increasing circuit absorbs heat from the electronic control device 16, the temperature of the gas-liquid two-phase refrigerant increases, and the amount of gaseous refrigerant increases. This allows more gaseous refrigerant to enter the compressor 11 and participate in the circulation, increasing the refrigerant circulation volume in the HVAC system and thus improving the start-up speed of the HVAC system. Therefore, under the second preset conditions, using the second preset control strategy to control the HVAC system not only achieves heat dissipation from the electronic control device 16, but also allows the refrigerant in the enthalpy-increasing circuit to recover the heat emitted by the electronic control device 16, increasing the refrigerant circulation volume in the HVAC system and improving the start-up speed of the HVAC system.

[0154] In one embodiment, controlling the HVAC system using a second preset control strategy may further include: increasing the opening of the first expansion valve E1 so that the temperature of the electronic control device 16 is lower than the second preset temperature, based on the temperature of the electronic control device 16 being greater than the second preset temperature.

[0155] It is understood that the electronic control device 16 includes multiple electronic components, each with a normal operating temperature range. The second preset temperature can be the maximum temperature allowed for the electronic control device 16 to operate normally. The second preset temperature is typically greater than 70°C; for example, it can be set to 75°C.

[0156] When the temperature of the electronic control device 16 is higher than the second preset temperature, it indicates that the temperature of the electronic control device 16 is too high and needs to be cooled down immediately. At this time, increasing the opening of the first expansion valve E1 can allow more two-phase refrigerant to flow through the heat dissipation pipe 15, which can quickly cool down the electronic control device 16 and reduce its temperature to below the second preset temperature, thus preventing damage to the electronic control device 16.

[0157] When the temperature of the electronic control device 16 is less than or equal to the second preset temperature, the second preset control strategy is used to control the HVAC system. This also includes step S222, where, based on the temperature of the electronic control device being less than or equal to the second preset temperature, the opening degree of the first expansion valve is controlled according to the auxiliary circuit superheat and the current target superheat, so that the auxiliary circuit superheat matches the current target superheat. The auxiliary circuit superheat is the difference between the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe 15 and the inlet temperature of the heat dissipation pipe.

[0158] The auxiliary superheat is a value actually obtained during the operation of the HVAC system. For example, during the operation of the HVAC system, the difference between the refrigerant temperature at the preset position after the outlet of the heat dissipation pipe 15 and the inlet temperature of the heat dissipation pipe 15 is the auxiliary superheat.

[0159] The target superheat can be defined as the difference between the refrigerant temperature at a preset location after the outlet of the heat dissipation pipe 15 in the HVAC system and the target temperature at the inlet of the heat dissipation pipe 15. The target temperature difference is usually an expected value. In the HVAC system, the target superheat can be used to control and regulate the circuit containing the heat dissipation pipe 15. When the auxiliary superheat matches the target superheat, it is beneficial to improve the efficiency and performance of the HVAC system.

[0160] The current target superheat is the target superheat of the HVAC system during its current operation, or in other words, the current target superheat is the current value of the target superheat when step S222 is executed. Under the second preset condition, the current target superheat can be used to control and regulate the first expansion valve E1 of the HVAC system.

[0161] Under the first preset condition, the target superheat setting is usually the current target superheat. Under the second preset condition, the current target superheat may differ from the target superheat setting.

[0162] In this embodiment of the disclosure, when the temperature of the electronic control device 16 is less than or equal to the second preset temperature, the opening degree of the first expansion valve E1 is controlled based on the auxiliary circuit superheat and the current target superheat, so that the auxiliary circuit superheat can be matched with the current target superheat, thereby improving the efficiency and performance of the HVAC system.

[0163] When the second preset control strategy is used to control the HVAC system, the opening of the first expansion valve E1 is controlled based on the auxiliary circuit superheat and the current target superheat, including: increasing the opening of the first expansion valve E1 when the auxiliary circuit superheat is greater than the current target superheat; or maintaining the opening of the first expansion valve E1 when the auxiliary circuit superheat is equal to the current target superheat; or decreasing the opening of the first expansion valve E1 when the auxiliary circuit superheat is less than the current target superheat.

[0164] When the overheat of the auxiliary road exceeds the current target overheat, refer to Figure 8 This can increase the opening of the first expansion valve E1, allowing more refrigerant to flow through the first expansion valve E1, and thus allowing more gas-liquid two-phase refrigerant to flow through the heat dissipation pipe 15, improving the cooling effect of the two-phase refrigerant. As a result, the refrigerant temperature at the preset position after the outlet of the heat dissipation pipe 15 can be reduced, reducing the superheat of the auxiliary circuit, so that the superheat of the auxiliary circuit matches the current target superheat.

[0165] When the auxiliary circuit overheat is less than the current target overheat, refer to Figure 8This can reduce the opening of the first expansion valve E1, allowing less refrigerant to flow through it, and consequently, less gas-liquid two-phase refrigerant to flow through the heat dissipation pipe 15, thus reducing the cooling effect of the two-phase refrigerant. This, in turn, can increase the refrigerant temperature at the preset position after the outlet of the heat dissipation pipe 15, increasing the superheat of the auxiliary circuit, and making the superheat of the auxiliary circuit match the current target superheat.

[0166] When the auxiliary circuit overheat equals the target overheat, refer to Figure 8 Maintain the opening of the first expansion valve E1. It should be noted that the auxiliary circuit superheat is equal to the current target superheat, which can be understood as the difference between the auxiliary circuit superheat and the current target superheat being within a preset range (e.g., an error range), or the auxiliary circuit superheat matching the current target superheat.

[0167] Under the first preset condition, the target superheat setting is usually the current target superheat. Under the second preset condition, the current target superheat may differ from the target superheat setting.

[0168] In one embodiment, the second preset control strategy is used to control the HVAC system, which further includes step S223, in which the current target superheat is determined based on the exhaust superheat of the HVAC system and the initial target superheat.

[0169] Under the first preset condition, the target superheat is typically set based on experience. Under the second preset condition, the target superheat can be set based on experience. Since the ambient temperature is relatively low under the second preset condition, during the operation of the HVAC system, the target superheat can be corrected based on the exhaust superheat and the initial target superheat. The corrected target superheat can be called the current target superheat, and the original target superheat can be called the initial target superheat. The current target superheat is used to control and adjust the first expansion valve E1 in the circuit containing the heat dissipation pipe 15 of the HVAC system, so that the auxiliary circuit superheat matches the current target superheat, improving the efficiency and performance of the HVAC system. Therefore, the current target superheat can be understood as the target superheat used to control and adjust the first expansion valve E1 of the HVAC system under the second preset condition.

[0170] Typically, before the HVAC system is put into operation, a target superheat setting value can be set for the HVAC system based on experience. When the HVAC system is started, it operates according to the target superheat setting value.

[0171] Under the second preset condition, the initial target superheat may not meet the operating requirements of the HVAC system. Therefore, before controlling the opening of the first expansion valve E1, the target superheat can be corrected based on the exhaust superheat of the HVAC system and the initial target superheat. The corrected target superheat is the current target superheat, ensuring that the exhaust superheat of the HVAC system ultimately meets the preset range. Therefore, controlling the HVAC system using the second preset control strategy before controlling the opening of the first expansion valve E1 may also include step S223, where the current target superheat is determined based on the exhaust superheat of the HVAC system and the initial target superheat. Then, the opening of the first expansion valve E1 is controlled using the determined current target superheat. Therefore, step S223 can be located before step S222. In another embodiment, step S223 can be located after step S222.

[0172] The exhaust superheat of an HVAC system can be defined as the temperature difference between the compressor exhaust port temperature and the refrigerant saturation temperature corresponding to the compressor exhaust port pressure.

[0173] In one embodiment, step S223, determining the current target superheat based on the initial values ​​of the exhaust superheat of the HVAC system and the initial target superheat, includes: increasing the target superheat based on the initial target superheat if the exhaust superheat is less than a first preset value, and determining the increased target superheat as the current target superheat; or, determining the initial target superheat as the current target superheat if the exhaust superheat meets a preset range; or, decreasing the target superheat based on the initial target superheat if the exhaust superheat is greater than a second preset value, and determining the decreased target superheat as the current target superheat; wherein the second preset value is greater than the first preset value.

[0174] The first preset value can be in the range of 10℃ to 20℃, and can be any value within that range. The second preset value can be in the range of greater than 30℃, and can be any value greater than 30℃. The preset range can be the interval determined by the first and second preset values.

[0175] When the exhaust superheat is less than a first preset value, the exhaust port temperature of compressor 11 is too low, which is detrimental to the operation of compressor 11. Therefore, the target superheat needs to be increased based on the initial target superheat, and the increased target superheat is determined as the current target superheat. For example, increasing the target superheat based on the initial target superheat can be achieved by adding 1°C. In other embodiments, the specific value added can be set as needed and is not limited to an increase of 1°C. The increased target superheat is then determined as the current target superheat.

[0176] When the exhaust superheat exceeds a second preset value, the exhaust port temperature of compressor 11 becomes too high, which is detrimental to the operation of compressor 11. Therefore, the target superheat needs to be reduced from the initial target superheat, and the reduced target superheat is determined as the current target superheat. For example, reducing the target superheat by 1°C from the initial target superheat can yield the reduced target superheat. In other embodiments, the specific reduction value can be set as needed and is not limited to a reduction of 1°C. The reduced target superheat is then determined as the current target superheat.

[0177] The opening of the first expansion valve E1 is adjusted according to the current target superheat, so that the auxiliary circuit superheat is equal to the current target superheat.

[0178] If the exhaust superheat meets the preset range, the initial target superheat can be set as the current target superheat.

[0179] It should be noted that during the operation of the HVAC system, steps S223 and S222 can be executed multiple times in a loop. Each execution follows the sequence S222, S223; or, alternatively, S223, S222. The current target superheat during this execution can be used as the initial target superheat for the next execution. For example, steps S223 and S222 can be executed every preset time interval, such as every 3 seconds, to ensure that the exhaust superheat during HVAC system operation meets a preset range and that the auxiliary circuit superheat matches the current target superheat. During the first execution of steps S223 and S222, the initial target superheat is the set value of the target superheat.

[0180] For example, when the outlet of compressor 11 is connected to the inlet of heat dissipation pipe 15 through the second solenoid valve V2, the first expansion valve E1 is opened and the first solenoid valve V1 is closed, while the second solenoid valve V2 is closed, thereby ensuring that a portion of the refrigerant flows through the first expansion valve E1, heat dissipation pipe 15, auxiliary pipe 132 of subcooler 132 and flows to the enthalpy injection port of compressor 11.

[0181] It is easy to understand that under the second preset condition, the ambient temperature is very low. In low-temperature heating operation, if the ambient temperature is -30℃, the evaporation temperature may be lower than -30℃, causing the temperature of the refrigerant entering the heat dissipation pipe 15 to be lower than -30℃. Furthermore, during startup, the heat generated by the components in the electronic control device 16 is relatively small, which may cause the component temperature to drop below -30℃, exceeding the component's allowable operating range (the allowable operating temperature for some components is -20℃ to 85℃), leading to difficulties in starting the HVAC system.

[0182] In one embodiment, before controlling the opening of the first expansion valve E1 and the closing of the first solenoid valve V1, i.e., before step S221, the HVAC system is controlled using a second preset control strategy, further including step S224. The HVAC system may include startup operation and normal operation. Startup operation may include step S224, and normal operation may include steps S221, S223, and S222. During normal operation, steps S223 and S222 may be executed repeatedly. Each time, the execution order is S222, S223; or, each time, the execution order is S223, S222.

[0183] In step S224, the first expansion valve E1 is closed, and both the first solenoid valve V1 and the second solenoid valve V2 are open, causing a portion of the refrigerant flowing out of the compressor 11 to flow through the second solenoid valve V2, the heat dissipation pipe 15, the auxiliary pipe 132 of the subcooler, and the first solenoid valve V1, and then to the inlet of the gas-liquid separator 12. This circuit, where a portion of the refrigerant flowing out of the compressor 11 flows through the second solenoid valve V2, the heat dissipation pipe 15, the auxiliary pipe 132 of the subcooler, and the first solenoid valve V1, and then to the inlet of the gas-liquid separator 12, can be called a hot gas bypass circuit. The hot gas bypass circuit includes: compressor discharge port → second solenoid valve → heat dissipation pipe → auxiliary pipe of the subcooler → first solenoid valve → gas-liquid separator inlet.

[0184] In this way, the refrigerant flowing out of the compressor 11 has a higher temperature. The use of a higher temperature refrigerant flowing through the heat dissipation pipe 15 can heat the electronic control device 16, allowing the electronic control device 16 to work at a suitable temperature, which is beneficial to improving the start-up speed of the HVAC system.

[0185] In this embodiment of the present disclosure, under the second preset condition, the ambient temperature is low. Step S224 can be used to control the first expansion valve E1 to be closed and control both the first solenoid valve V1 and the second solenoid valve V2 to be open. This allows a portion of the refrigerant flowing out of the compressor 11 to flow through the second solenoid valve V2, the heat dissipation pipe 15, the auxiliary pipe 132 of the subcooler, and the first solenoid valve V1, and then flow to the inlet of the gas-liquid separator 12. As a result, the higher-temperature refrigerant flowing out of the compressor 11 can heat the electronic control device 16, allowing the electronic control device 16 to operate at a suitable temperature. At the same time, the refrigerant can absorb the heat emitted by the components and recover the heat from the components, increasing the refrigerant circulation volume and improving the start-up speed of the HVAC system.

[0186] After the HVAC system is started, steps S221, S223, and S222 can be used to control the HVAC system. The gas-liquid two-phase refrigerant in the enthalpy-increasing circuit can absorb the heat from the electronic control device 16 and cool the electronic control device 16. After the refrigerant in the enthalpy-increasing circuit absorbs the heat from the electronic control device 16, the temperature of the gas-liquid two-phase refrigerant can be increased, and the amount of gaseous refrigerant can be increased. This allows more gaseous refrigerant to enter the compressor 11 to participate in the circulation, thereby increasing the amount of refrigerant circulating in the HVAC system and improving the heating effect of the HVAC system.

[0187] The technical solution of this embodiment, under the second preset condition, i.e., the HVAC system operates in a low-temperature heating condition, employs a hot gas bypass circuit to introduce heat dissipation pipe 15. By using the relatively high-temperature refrigerant (approximately 10°C) discharged from compressor 11 to heat the electronic control device 16, the components in the electronic control device 16 can be kept at a suitable temperature. Simultaneously, the refrigerant can absorb and recover the heat emitted by the components, increasing the refrigerant circulation volume and improving the start-up speed. As the HVAC system completes startup, the discharge temperature of compressor 11 gradually increases, and the heat generation of the components increases. At this point, the heat dissipation capacity of the discharge temperature decreases and cannot meet the heat dissipation requirements of the components. Therefore, after the HVAC system is started, the hot gas bypass circuit can be closed, that is, the second solenoid valve V2 is turned off, the first solenoid valve V1 is turned off, and the first expansion valve E1 is opened. The circuit where the heat dissipation pipe 15 is located is switched to the enthalpy injection circuit, and two-phase refrigerant is used to dissipate heat from the electronic control device 16. This increases the evaporation temperature of the heat dissipation pipe 15, prevents the evaporation temperature from falling below the ambient temperature, and prevents the component temperature from cooling below the first preset temperature, ensuring that the components in the electronic control device 16 are within the allowable operating range.

[0188] In one embodiment, startup can satisfy a preset time strategy, that is, the state where the first expansion valve E1 is closed and both the first solenoid valve V1 and the second solenoid valve V2 are open satisfies the preset time strategy. After startup satisfies the preset time strategy, startup is complete, and the HVAC system enters normal operation.

[0189] In one embodiment, the preset time strategy includes maintaining the system for a first preset duration if the exhaust superheat of the HVAC system exceeds a first preset value. During startup, the exhaust superheat of the HVAC system can be acquired. If the exhaust superheat exceeds the first preset value, then the first expansion valve E1 is closed, and both the first solenoid valve V1 and the second solenoid valve V2 are open, maintaining this state for the first preset duration. The HVAC system then completes startup and enters normal operation. For example, the first preset duration can be greater than or equal to 5 minutes. The first preset duration can also be set as needed and is not limited to being greater than or equal to 5 minutes.

[0190] In another embodiment, the preset time strategy includes a duration longer than a second preset time. When the exhaust superheat of the HVAC system is less than a first preset value, the preset time strategy can be longer than the second preset time, i.e., the startup time is longer than the second preset time. In other words, the duration of the state where the first expansion valve E1 is closed and both the first solenoid valve V1 and the second solenoid valve V2 are open is longer than the second preset time, at which point the HVAC system completes startup, and subsequently enters normal operation. For example, the range of the second preset time is 10 minutes to 30 minutes. The specific duration of the second preset time can be set according to actual needs.

[0191] Figure 9 This is a pressure-enthalpy diagram of the HVAC system in heating mode. Figure 9 The diagram shows position C of the electronic control device 16 in the heating mode using two-phase refrigerant for heat dissipation in this embodiment of the present disclosure. When the ambient temperature is lower than the first preset temperature, due to step S224, the electronic control device 16 dissipates heat at position C, where the temperature is approximately 10°C.

[0192] Figure 10 This is a flowchart of a control method for a heating, ventilation, and air conditioning system according to an embodiment of this disclosure. The following is in conjunction with... Figure 10 The process of the control method disclosed herein is briefly described.

[0193] like Figure 10 As shown, the system detects the operating mode and ambient temperature. When the operating mode is cooling mode, or the operating mode is heating mode and the ambient temperature is greater than or equal to the first preset temperature, the first preset condition is met, and the first preset control strategy is used to control the HVAC system. Under the first preset control strategy, the startup and control operation of the HVAC system use the same control method.

[0194] In the first preset control strategy, the second solenoid valve V2 is turned off, the first solenoid valve V1 is turned on, and the first expansion valve E1 is opened. Based on the auxiliary circuit superheat and the target superheat, the opening degree of the first expansion valve E1 is controlled. The process of controlling the opening degree of the first expansion valve E1 has been explained in detail above and will not be repeated here.

[0195] When the operating mode is heating mode and the ambient temperature is lower than the first preset temperature, the second preset condition is met, and the second preset control strategy is used to control the HVAC system. In the second preset control strategy, the start-up operation and normal operation of the HVAC system use different control methods.

[0196] During startup, the first expansion valve E1 is shut off, the first solenoid valve V1 is turned on, and the second solenoid valve V2 is turned on, opening the hot gas bypass circuit, which then flows to the inlet of the gas-liquid separator 12. The preset time strategy required for startup has been described in detail above and will not be repeated here.

[0197] During normal operation, the first solenoid valve V1 is turned off, the second solenoid valve V2 is turned off, and the first expansion valve E1 is turned on. The circuit where the heat dissipation pipe 15 is located is switched to the enthalpy injection circuit, and medium-pressure refrigerant is used to dissipate heat from the electronic control device 16.

[0198] During normal operation, the target superheat has a set value. The target superheat is corrected by the exhaust superheat to obtain the current target superheat. Based on the auxiliary circuit superheat and the current target superheat, the opening of the first expansion valve E1 is controlled. The specific process has been explained in detail above and will not be repeated here.

[0199] This disclosure also provides a control device for a heating, ventilation, and air conditioning (HVAC) system. The HVAC system includes the compressor module 10 in any embodiment of this disclosure. The control device is configured to implement the control method of any embodiment of this disclosure. An electronic control device 16 may include the control device, or the electronic control device 16 may be the control device itself, and the electronic control device 16 is configured to implement the control method of this disclosure.

[0200] According to embodiments of this disclosure, this disclosure also provides an electronic device. The electronic device, such as... Figure 11 As shown, it includes: at least one processor 502; and a memory 501 communicatively connected to the at least one processor 502. The memory 501 stores instructions executable by the at least one processor 502, which, when executed, enable the at least one processor 502 to perform the control method of any embodiment of this disclosure. The electronic control device 16 may include this electronic device.

[0201] This disclosure also provides a readable storage medium storing a computer program that, when executed by a processor, implements the control method as described in any embodiment of this disclosure.

[0202] This disclosure also provides a heating, ventilation, and air conditioning (HVAC) system, including the compressor module 10 of any embodiment of this disclosure. The HVAC system also includes the control device of any embodiment of this disclosure or the electronic device of this disclosure.

[0203] refer to Figure 5 and Figure 6 The HVAC system may also include a first heat exchange module 20 and a second heat exchange module 30. The first heat exchange module 20 includes at least one first heat exchange module 21. When the first heat exchange module 20 includes multiple first heat exchange modules 21, the multiple first heat exchange modules 21 are connected in parallel. The first port of the first heat exchange module 20 is connected to the four-way valve 17 in the compressor module 10 through a first pipe 41, and the second port of the first heat exchange module 20 is connected to the first port of the transfer pipe 42.

[0204] The second heat exchange module 30 includes at least one second heat exchange module 31. When the second heat exchange module 30 includes multiple second heat exchange modules 31, the multiple second heat exchange modules 31 are connected in parallel. The second port of the transfer pipe 42 is connected to the first port of the second heat exchange module 30 through the third pipe 43, and the second port of the second heat exchange module 30 is connected to the four-way valve 17 in the compressor module 10 through the second pipe 44.

[0205] Various embodiments of the systems and techniques described above herein can be implemented in digital electronic circuit systems, integrated circuit systems, field-programmable gate arrays (FPGAs), application-specific integrated circuits (ASICs), application-specific standard products (ASSPs), systems-on-a-chip (SoCs), payload-programmable logic devices (CPLDs), computer hardware, firmware, software, and / or combinations thereof. These various embodiments may include implementations in one or more computer programs that can be executed and / or interpreted on a programmable system including at least one programmable processor, which may be a dedicated or general-purpose programmable processor, capable of receiving data and instructions from a storage system, at least one input device, and at least one output device, and transmitting data and instructions to the storage system, the at least one input device, and the at least one output device.

[0206] The program code used to implement the methods of this disclosure may be written in any combination of one or more programming languages. This program code may be provided to a processor or controller of a general-purpose computer, special-purpose computer, or other programmable data processing apparatus, such that when executed by the processor or controller, the program code causes the functions / operations specified in the flowcharts and / or block diagrams to be implemented. The program code may be executed entirely on a machine, partially on a machine, as a standalone software package partially on a machine and partially on a remote machine, or entirely on a remote machine or server.

[0207] In the context of this disclosure, a machine-readable medium can be a tangible medium that may contain or store a program for use by or in conjunction with an instruction execution system, apparatus, or device. A machine-readable medium can be a machine-readable signal medium or a machine-readable storage medium. A machine-readable medium can be, but is not limited to, electronic, magnetic, optical, electromagnetic, infrared, or semiconductor systems, apparatus, or devices, or any suitable combination of the foregoing. More specific examples of machine-readable storage media include electrical connections based on one or more wires, portable computer disks, hard disks, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical fiber, portable compact disk read-only memory (CD-ROM), optical storage devices, magnetic storage devices, or any suitable combination of the foregoing.

[0208] To provide interaction with a user, the systems and techniques described herein can be implemented on a computer having: a display device for displaying information to the user (e.g., a CRT (cathode ray tube) or LCD (liquid crystal display) monitor); and a keyboard and pointing device (e.g., a mouse or trackball) through which the user provides input to the computer. Other types of devices can also be used to provide interaction with the user; for example, feedback provided to the user can be any form of sensory feedback (e.g., visual feedback, auditory feedback, or tactile feedback); and input from the user can be received in any form (including sound input, voice input, or tactile input).

[0209] The systems and technologies described herein can be implemented in computing systems that include backend components (e.g., as a data server), or computing systems that include middleware components (e.g., an application server), or computing systems that include frontend components (e.g., a user computer with a graphical user interface or web browser through which a user can interact with embodiments of the systems and technologies described herein), or any combination of such backend, middleware, or frontend components. The components of the system can be interconnected via digital data communication of any form or medium (e.g., a communication network). Examples of communication networks include local area networks (LANs), wide area networks (WANs), and the Internet.

[0210] Computer systems can include clients and servers. Clients and servers are generally located far apart and typically interact via communication networks. Client-server relationships are created by computer programs running on the respective computers and having a client-server relationship with each other. Servers can be cloud servers, servers in distributed systems, or servers incorporating blockchain technology.

[0211] It should be understood that the various forms of processes shown above can be used to rearrange, add, or delete steps. For example, the steps described in this disclosure can be executed in parallel, sequentially, or in different orders, as long as the desired result of the technical solution disclosed in this disclosure can be achieved, and this is not limited herein.

[0212] In the description of this specification, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this disclosure, "multiple" means two or more, unless otherwise expressly specified.

[0213] In this disclosure, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or a connection via piping, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection via an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this disclosure according to the specific circumstances.

[0214] In this disclosure, unless otherwise expressly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0215] The foregoing disclosure provides many different implementations or examples for carrying out different structures of this disclosure. To simplify this disclosure, the components and arrangements of specific examples are described above. Of course, these are merely examples and are not intended to limit this disclosure. Furthermore, reference numerals and / or reference letters may be repeated in different examples; such repetition is for simplification and clarity and does not in itself indicate a relationship between the various implementations and / or arrangements discussed.

[0216] The specific embodiments described above do not constitute a limitation on the scope of protection of this disclosure. Those skilled in the art should understand that various modifications, combinations, sub-combinations, and substitutions can be made according to design requirements and other factors. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this disclosure should be included within the scope of protection of this disclosure.

Claims

1. A compressor module, characterized in that, It includes a compressor, a gas-liquid separator, a transfer pipeline, a first expansion valve, and a heat dissipation pipe, wherein the heat dissipation pipe is used to dissipate heat from the electrical control device of the heating and ventilation system; The first port of the transfer pipe is used to connect to the first heat exchange module of the HVAC system, and the second port of the transfer pipe is used to connect to the second heat exchange module of the HVAC system. A first branch pipe is provided between the first port and the second port of the transfer pipe. The first branch pipe is connected to the inlet of the first expansion valve, and the outlet of the first expansion valve is connected to the inlet of the heat dissipation pipe through a first branch pipe. The outlet of the heat dissipation pipe is connected to the suction port of the compressor through the gas-liquid separator; and / or, the outlet of the heat dissipation pipe is connected to the enthalpy injection port of the compressor. The outlet of the first expansion valve is also connected to one end of the second solenoid valve through a second branch pipe, and the other end of the second solenoid valve is connected to the exhaust port of the compressor.

2. The compressor module according to claim 1, characterized in that, A first solenoid valve is provided between the outlet of the heat dissipation pipe and the inlet of the gas-liquid separator. The first solenoid valve is configured to open under a first preset condition, so that the refrigerant flowing out of the outlet of the heat dissipation pipe flows through the first solenoid valve and flows to the gas-liquid separator; The first solenoid valve is also configured to shut off under a second preset condition, so that the refrigerant flowing out of the outlet of the heat dissipation pipe flows to the enthalpy injection port of the compressor.

3. The compressor module according to claim 1, characterized in that, The second solenoid valve is configured to satisfy a preset time strategy when it is in the conducting state under a second preset condition, and the first expansion valve is configured to be closed when the second solenoid valve is in the conducting state, so that a portion of the refrigerant flowing out of the compressor's exhaust port flows through the second solenoid valve and the heat dissipation pipe and flows to the gas-liquid separator.

4. The compressor module according to claim 2 or 3, characterized in that, The first preset condition includes at least one of the following: the HVAC system is operating in cooling mode; the HVAC system is operating in heating mode and the ambient temperature is greater than or equal to the first preset temperature; and / or, The second preset condition includes the HVAC system operating in heating mode and the ambient temperature being lower than the first preset temperature.

5. The compressor module according to claim 1, characterized in that, The compressor module further includes a first temperature sensor for detecting the inlet temperature of the heat dissipation pipe and a second temperature sensor for detecting the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe. The opening degree of the first expansion valve is determined based on the temperature difference between the second temperature sensor and the first temperature sensor.

6. The compressor module according to claim 1, characterized in that, The first expansion valve can convert the refrigerant flowing through it into a two-phase refrigerant, which flows through the heat dissipation pipe to dissipate heat from the electronic control device.

7. The compressor module according to claim 1, characterized in that, It also includes a subcooler, which includes a main pipeline, which is disposed between the first port of the transfer pipeline and the first branch pipeline; The subcooler also includes an auxiliary pipeline, which includes at least a connecting section. The outlet of the heat dissipation pipe is connected to the gas-liquid separator through the connecting section; and / or, the outlet of the heat dissipation pipe is connected to the enthalpy injection port of the compressor through the connecting section.

8. The compressor module according to claim 7, characterized in that, The auxiliary pipeline also includes the heat dissipation pipe.

9. A control method for a heating, ventilation, and air conditioning system, characterized in that, The HVAC system includes the compressor module according to any one of claims 1-8, and the control method includes: Determine the operating conditions of the HVAC system, the operating conditions including a first preset condition and a second preset condition; The HVAC system is controlled by a first preset control strategy based on the first preset condition; or, the HVAC system is controlled by a second preset control strategy based on the second preset condition.

10. The method according to claim 9, characterized in that, The HVAC system is controlled using a first preset control strategy, including: By controlling the opening of the first expansion valve and the activation of the first solenoid valve, at least a portion of the refrigerant in the transfer pipeline flows through the first expansion valve, the heat dissipation pipe, and the first solenoid valve, and flows to the gas-liquid separator.

11. The method according to claim 10, characterized in that, The method of controlling the HVAC system using a first preset control strategy further includes: Based on the auxiliary superheat and the target superheat, the opening of the first expansion valve is controlled so that the auxiliary superheat matches the target superheat. The auxiliary superheat is the difference between the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe and the inlet temperature of the heat dissipation pipe.

12. The method according to claim 10, characterized in that, Based on the auxiliary superheat and the target superheat, the opening degree of the first expansion valve is controlled, including: If the auxiliary circuit superheat is greater than the target superheat, increase the opening of the first expansion valve; or, Based on the fact that the auxiliary circuit superheat equals the target superheat, maintain the opening of the first expansion valve; or, If the superheat of the auxiliary circuit is less than the target superheat, reduce the opening of the first expansion valve.

13. The method according to claim 9, characterized in that, The HVAC system is controlled using a second preset control strategy, including: The first expansion valve is opened and the first solenoid valve is closed, so that at least a portion of the refrigerant in the transfer pipeline flows through the first expansion valve and the heat dissipation pipe and flows to the enthalpy injection port of the compressor.

14. The method according to claim 13, characterized in that, The second preset control strategy for controlling the HVAC system further includes: If the temperature of the electronic control device is greater than the second preset temperature, the opening of the first expansion valve is increased so that the temperature of the electronic control device is less than or equal to the second preset temperature.

15. The method according to claim 13, characterized in that, The second preset control strategy for controlling the HVAC system further includes: Based on the temperature of the electronic control device being less than or equal to the second preset temperature, and based on the auxiliary circuit superheat and the current target superheat, the opening of the first expansion valve is controlled so that the auxiliary circuit superheat matches the current target superheat. The auxiliary circuit superheat is the difference between the refrigerant temperature at a preset position after the outlet of the heat dissipation pipe and the inlet temperature of the heat dissipation pipe.

16. The method according to claim 15, characterized in that, Based on the auxiliary circuit superheat and the current target superheat, the opening degree of the first expansion valve is controlled, including: If the auxiliary circuit superheat is greater than the current target superheat, increase the opening of the first expansion valve; or, Based on the fact that the auxiliary circuit superheat is equal to the current target superheat, maintain the opening of the first expansion valve; or, If the auxiliary circuit superheat is less than the current target superheat, reduce the opening of the first expansion valve.

17. The method according to claim 15, characterized in that, The second preset control strategy for controlling the HVAC system further includes: The current target superheat is determined based on the exhaust superheat of the HVAC system and the initial target superheat.

18. The method according to claim 17, characterized in that, Based on the exhaust superheat of the HVAC system and the initial target superheat, determine the current target superheat, including: If the exhaust superheat is less than a first preset value, the target superheat is increased based on the initial target superheat, and the increased target superheat is determined as the current target superheat; or... Based on the condition that the exhaust superheat meets a preset range, the initial target superheat is determined as the current target superheat; or... Based on the fact that the exhaust superheat is greater than the second preset value, the target superheat is reduced based on the initial target superheat, and the reduced target superheat is determined as the current target superheat. Wherein, the second preset value is greater than the first preset value.

19. The method according to claim 13, characterized in that, Before controlling the opening of the first expansion valve and the closing of the first solenoid valve, the second preset control strategy is used to control the HVAC system, which further includes: The first expansion valve is controlled to close, and both the first and second solenoid valves are controlled to open, so that a portion of the refrigerant flowing out of the compressor's exhaust port flows through the second solenoid valve, the heat dissipation pipe, and the first solenoid valve and flows to the inlet of the gas-liquid separator.

20. The method according to claim 19, characterized in that, The control of the first expansion valve being closed and the first and second solenoid valves being both open satisfies a preset time strategy.

21. The method according to claim 20, characterized in that, The preset time strategy includes maintaining the system for a first preset duration when the exhaust superheat of the HVAC system is greater than a first preset value; or... The preset time strategy includes a duration greater than the second preset duration.

22. The method according to claim 21, characterized in that, The first preset duration is greater than or equal to 5 minutes; or, the second preset duration is in the range of 10 minutes to 30 minutes.

23. The method according to claim 9, characterized in that, Determining the operating conditions of the HVAC system includes: Obtain the operating mode and ambient temperature of the HVAC system; Based on the operating mode being cooling mode, the HVAC system is determined to meet the first preset condition; or, based on the operating mode being heating mode and the ambient temperature being greater than or equal to the first preset temperature, the HVAC system is determined to meet the first preset condition; or, based on the operating mode being heating mode and the ambient temperature being less than the first preset temperature, the HVAC system is determined to meet the second preset condition.

24. A control device for a heating, ventilation, and air conditioning system, characterized in that, The HVAC system includes a compressor module according to any one of claims 1-8, and the control device is configured to implement the control method according to any one of claims 9-23.

25. An electronic device, characterized in that, include: At least one processor; as well as A memory communicatively connected to the at least one processor; wherein, The memory stores instructions that can be executed by the at least one processor to enable the at least one processor to perform the control method according to any one of claims 9-23.

26. A heating, ventilation, and air conditioning system, characterized in that, The device includes the compressor module according to any one of claims 1-8, and further includes the control device according to claim 24 or the electronic device according to claim 25.

27. The HVAC system according to claim 26, characterized in that, Also includes: A first heat exchange module includes at least one first heat exchange module. When the first heat exchange module includes multiple first heat exchange modules, the multiple first heat exchange modules are connected in parallel. The first port of the first heat exchange module is connected to a four-way valve in the compressor module through a first pipeline. The second port of the first heat exchange module is connected to a first port of a transfer pipeline; and / or... The second heat exchange module includes at least one second heat exchange module. When the second heat exchange module includes multiple second heat exchange modules, the multiple second heat exchange modules are connected in parallel. The second port of the transfer pipeline is connected to the first port of the second heat exchange module through a third pipeline. The second port of the second heat exchange module is connected to the four-way valve in the compressor module through a second pipeline.

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