Control method and control device of air conditioning system, air conditioning system and storage medium

Abstract

The application discloses a control method and device of an air conditioning system, the air conditioning system and a computer readable storage medium. The air conditioning system comprises an indoor unit and an outdoor unit, the indoor unit comprises an indoor heat exchanger and a first valve, the outdoor unit comprises an outdoor heat exchanger and a compressor, the indoor heat exchanger, the first valve, the outdoor heat exchanger and the compressor are communicated through pipelines to form a refrigerant circulation loop; the control method comprises the following steps: when the air conditioning system is in a refrigeration mode, determining a temperature correction amount according to an outlet temperature of the indoor heat exchanger and a suction temperature of the compressor; determining a suction superheat according to the suction temperature of the compressor, a suction pressure of the compressor and the temperature correction amount; and controlling an opening degree of the first valve according to the suction superheat. In the control method, the accuracy of the first valve in adjusting the refrigerant flow can be improved, and the operation stability and energy efficiency of the air conditioning system can be improved.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and in particular to a control method, control device, air conditioning system, and computer-readable storage medium for an air conditioning system. Background Technology

[0002] In related technologies, multi-split air conditioning systems typically control refrigerant flow by detecting the compressor's suction temperature and pressure, calculating the suction superheat based on the saturation temperature corresponding to the suction pressure, and adjusting the opening of the indoor unit's electronic expansion valve according to the suction superheat. However, during the cooling operation of a multi-split air conditioning system, using the compressor suction temperature to calculate the suction superheat can easily lead to an underestimation of the calculated suction superheat, resulting in an excessive reduction in the electronic expansion valve opening and affecting the cooling capacity and operational efficiency of the air conditioning system. Summary of the Invention

[0003] The present invention provides a control method, control device, air conditioning system, and computer-readable storage medium for an air conditioning system to solve at least one of the aforementioned technical problems.

[0004] This invention provides a control method for an air conditioning system, the air conditioning system including an indoor unit and an outdoor unit, the indoor unit including an indoor heat exchanger and a first valve, the outdoor unit including an outdoor heat exchanger and a compressor, the indoor heat exchanger, the first valve, the outdoor heat exchanger and the compressor being connected by pipelines to form a refrigerant circulation loop; The control method includes: When the air conditioning system is in cooling mode, the temperature correction amount is determined based on the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor. The suction superheat is determined based on the compressor's suction temperature, the compressor's suction pressure, and the temperature correction amount. The opening degree of the first valve is controlled according to the intake superheat.

[0005] In the above control method, the temperature correction amount is determined based on the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor. Then, the suction superheat is determined based on the temperature correction amount and the suction pressure of the compressor. This reduces the calculation deviation of suction superheat caused by the temperature drop of the refrigerant during the return process, making the obtained suction superheat closer to the actual superheat state of the refrigerant at the outlet of the indoor heat exchanger. At the same time, it takes into account the actual operating state of the compressor inlet, thereby improving the accuracy of suction superheat. This, in turn, improves the accuracy of the first valve in regulating the refrigerant flow, and improves the operational stability and energy efficiency of the air conditioning system.

[0006] In some embodiments, determining the temperature correction amount based on the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor includes: When the outlet temperature of the indoor heat exchanger is greater than or equal to the suction temperature of the compressor, the difference between the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor is determined as the temperature correction amount. When the outlet temperature of the indoor heat exchanger is lower than the suction temperature of the compressor, the temperature correction amount is determined to be zero.

[0007] In some embodiments, determining the suction superheat based on the compressor's suction temperature, the compressor's suction pressure, and the temperature correction amount includes: The corresponding saturation temperature is determined based on the suction pressure of the compressor; The suction superheat is determined based on the compressor's suction temperature, the saturation temperature, and the temperature correction amount.

[0008] In some embodiments, the intake superheat SH satisfies SH = T suc -T esat +k×T corr ; Among them, T suc T represents the suction temperature of the compressor. esat T represents the saturation temperature. corr The value represents the temperature correction amount, and k represents the correction coefficient.

[0009] In some implementations, the correction factor is between 0.25 and 0.8.

[0010] In some embodiments, controlling the opening degree of the first valve based on the intake superheat includes When the intake superheat is less than a first preset value, the opening of the first valve is reduced; When the intake superheat is greater than the second preset value, the opening of the first valve is increased; When the intake superheat is greater than or equal to the first preset value and less than or equal to the second preset value, the opening of the first valve remains unchanged.

[0011] In some implementations, the first preset value is 2°C to 5°C, and the second preset value is 6°C to 8°C.

[0012] An embodiment of the present invention provides a control device, including a processor and a memory, wherein the memory stores a computer program, and when the computer program is executed by the processor, it implements the control method described in any of the above embodiments.

[0013] An air conditioning system provided by an embodiment of the present invention includes an indoor unit, an outdoor unit, and a control device as described in the above embodiment. The indoor unit includes an indoor heat exchanger and a first valve, and the outdoor unit includes an outdoor heat exchanger and a compressor. The first valve and the compressor are both electrically connected to the control device.

[0014] The present invention provides a computer-readable storage medium having a computer program stored thereon, wherein the computer program, when executed by a processor, implements the control method described in any of the above embodiments.

[0015] Additional aspects and advantages of the invention will be set forth in the description which follows, and will become apparent from the description or may be learned by practice of the invention. Attached Figure Description

[0016] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, wherein: Figure 1 This is a flowchart illustrating the control method according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the air conditioning system in cooling mode according to an embodiment of the present invention; Figure 3 This is a schematic diagram of the air conditioning system in heating mode according to an embodiment of the present invention; Figure 4 This is a schematic diagram of another module of the air conditioning system according to an embodiment of the present invention.

[0017] Explanation of key component reference numerals: Air conditioning system 100, indoor unit 10, outdoor unit 20, second valve 30, third valve 40, control device 60, indoor heat exchanger 101, first valve 102, first temperature sensor 103, compressor 201, outdoor heat exchanger 203, fourth valve 204, four-way valve 206, one-way valve 207, third temperature sensor 208, second pressure sensor 209, second temperature sensor 210, first pressure sensor 211, gas-liquid separator 212, fourth temperature sensor 213, processor 601, memory 602. Detailed Implementation

[0018] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the embodiments of the present invention, and should not be construed as limiting the embodiments of the present invention.

[0019] Please see Figures 1 to 3 The present invention provides a control method for an air conditioning system 100, the air conditioning system 100 including an indoor unit 10 and an outdoor unit 20, the indoor unit 10 including an indoor heat exchanger 101 and a first valve 102, the outdoor unit 20 including an outdoor heat exchanger 203 and a compressor 201, the indoor heat exchanger 101, the first valve 102, the outdoor heat exchanger 203 and the compressor 201 are connected by pipelines to form a refrigerant circulation loop; Control methods include: Step S03: When the air conditioning system 100 is in cooling mode, determine the temperature correction amount based on the outlet temperature of the indoor heat exchanger 101 and the suction temperature of the compressor 201. Step S05: Determine the suction superheat based on the suction temperature of compressor 201, the suction pressure of compressor 201, and the temperature correction amount. Step S07: Control the opening degree of the first valve 102 according to the superheat of the intake air.

[0020] In the above control method, the temperature correction amount is determined based on the outlet temperature of the indoor heat exchanger 101 and the suction temperature of the compressor 201. Then, the suction superheat is determined based on the temperature correction amount and the suction pressure of the compressor 201. This can reduce the calculation deviation of suction superheat caused by the temperature drop of the refrigerant during the return process, making the obtained suction superheat closer to the actual superheat state of the refrigerant at the outlet of the indoor heat exchanger 101. At the same time, it takes into account the actual operating state of the compressor 201 inlet, thereby improving the accuracy of suction superheat, which in turn improves the accuracy of the first valve 102 in regulating the refrigerant flow, and improves the operational stability and energy efficiency of the air conditioning system 100.

[0021] Specifically, the air conditioning system 100 includes, but is not limited to, a multi-split air conditioning system 100. The air conditioning system 100 includes an indoor unit 10 and an outdoor unit 20. The indoor unit 10 includes an indoor heat exchanger 101 and a first valve 102. The indoor heat exchanger 101 is used to exchange heat with the indoor environment to achieve cooling or heating of the indoor air. The first valve 102 is located on a pipe connected to the indoor heat exchanger 101 and is used to regulate the flow rate of refrigerant flowing into the indoor heat exchanger 101, thereby regulating the heat exchange capacity of the indoor heat exchanger 101. The first valve 102 includes, but is not limited to, an electronic expansion valve. The outdoor unit 20 includes an outdoor heat exchanger 203 and a compressor 201. The compressor 201 is used to compress low-temperature gaseous refrigerant into high-temperature gaseous refrigerant and drive the refrigerant to circulate in the refrigerant circulation loop. The outdoor heat exchanger 203 is used to exchange heat with the outdoor environment to achieve heat exchange between the refrigerant and the external environment. In heating mode, the indoor heat exchanger 101 is used as a condenser, and the outdoor heat exchanger 203 is used as an evaporator. In cooling mode, the indoor heat exchanger 101 is used as an evaporator, and the refrigerant enters the indoor heat exchanger 101 through the first valve 102 for evaporation and heat exchange. The outdoor heat exchanger 203 is used as a condenser.

[0022] In one embodiment, the air conditioning system 100 further includes a second valve 30 and a third valve 40, through which the indoor unit 10 and the outdoor unit 20 are connected. The second valve 30 and the third valve 40 can control the connection state between the outdoor unit 20 and the indoor unit 10. The second valve 30 and the third valve 40 include, but are not limited to, solenoid valves.

[0023] In one embodiment, the outdoor unit 20 further includes a four-way valve 206, a one-way valve 207, a gas-liquid separator 212, and a fourth valve 204. The four-way valve 206 is used to switch the refrigerant flow direction to achieve switching between heating and cooling modes of the air conditioning system 100. The gas-liquid separator 212 is located at the inlet of the compressor 201 to separate liquid refrigerant from the return gas, ensuring that the refrigerant entering the compressor 201 is predominantly gaseous, thereby reducing the risk of liquid slugging in the compressor 201. The one-way valve 207 is located at the outlet of the compressor 201 to prevent refrigerant from entering the compressor 201 from the outlet, thereby protecting the compressor 201. The fourth valve 204 is located on the pipeline connected to the outdoor heat exchanger 203 and is used to regulate the refrigerant flow into the outdoor heat exchanger 203, thereby regulating the heat exchange capacity of the outdoor heat exchanger 203. The fourth valve 204 includes, but is not limited to, an electronic expansion valve.

[0024] During the operation of the air conditioning system 100, when the air conditioning system 100 is in control mode, such as Figure 2The compressor 201 draws in low-temperature, low-pressure gaseous refrigerant and compresses it to form high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is diverted through the four-way valve 206 and enters the outdoor heat exchanger 203, where it releases heat to the outdoor environment and condenses to form high-pressure liquid refrigerant. The high-pressure liquid refrigerant enters the indoor unit 10 through the third valve 40, and after being throttled and depressurized by the first valve 102, it absorbs heat from the indoor environment in the indoor heat exchanger 101 and evaporates to form low-temperature, low-pressure gaseous refrigerant. This gaseous refrigerant then returns to the compressor 201 inlet via the second valve 30, the four-way valve 206, and the gas-liquid separator 212, thus completing the refrigerant cycle.

[0025] When the air conditioning system 100 is in heating mode, such as Figure 3 The compressor 201 draws in low-temperature, low-pressure gaseous refrigerant and compresses it to form high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is diverted through the four-way valve 206 to the second valve 30 and delivered to the indoor unit 10. There, it exchanges heat with indoor air in the indoor heat exchanger 101, releasing heat to the indoor environment before condensing to form high-pressure liquid refrigerant. The high-pressure liquid refrigerant returns to the outdoor unit 20 through the third valve 40, and after being throttled and depressurized by the fourth valve 204, it enters the outdoor heat exchanger 203. In the outdoor heat exchanger 203, it absorbs heat from the outdoor environment and evaporates to form low-temperature, low-pressure gaseous refrigerant. This gaseous refrigerant then returns to the compressor 201 inlet via the four-way valve 206 and the gas-liquid separator 212, thus completing the refrigerant cycle for heating.

[0026] It should be noted that, since the connecting pipes between the indoor unit 10 and the outdoor unit 20 are usually quite long, and when the air conditioning system 100 includes multiple indoor units 10, these multiple indoor units 10 may be connected to the outdoor unit 20 through a branch pipe, when the air conditioning system 100 is in cooling mode, during the process of the refrigerant flowing from the outlet of the indoor heat exchanger 101 to the inlet of the compressor 201, the temperature may drop due to factors such as pipe resistance and heat absorption by the secondary evaporation of the refrigerant, causing the suction temperature of the compressor 201 to be lower than the outlet temperature of the indoor heat exchanger 101.

[0027] It is understood that suction superheat is used to characterize the degree of superheat of the refrigerant entering the compressor 201 relative to its saturated state. In this embodiment of the invention, by obtaining the outlet temperature of the indoor heat exchanger 101 and the suction temperature of the compressor 201, both the outlet state of the indoor heat exchanger 101 and the inlet state of the compressor 201 can be considered, resulting in a more accurate suction superheat. The outlet temperature of the indoor heat exchanger 101 reflects the heat exchange state of the refrigerant leaving the evaporator, while the suction temperature of the compressor 201 reflects the actual operating state of the refrigerant entering the compressor 201. By combining these two, the temperature change of the refrigerant during its flow from the outlet of the indoor heat exchanger 101 to the inlet of the compressor 201 can be characterized, thereby reducing the impact of temperature changes caused by excessively long return pipes or other reasons on the calculation of suction superheat. Furthermore, based on the obtained suction superheat as the control basis of the first valve 102, the adjustment of the first valve 102 can more accurately match the actual heat exchange requirements of the indoor heat exchanger 101, improving the stability and energy efficiency of the air conditioning system 100.

[0028] Optionally, the air conditioning system 100 includes a first temperature sensor 103, a second temperature sensor 210, a third temperature sensor 208, a fourth temperature sensor 213, a first pressure sensor 211, and a second pressure sensor 209. The first temperature sensor 103 is located at the outlet of the indoor heat exchanger 101 when it is used as an evaporator, and is used to detect the outlet temperature of the indoor heat exchanger 101; the second temperature sensor 210 is located at the inlet of the compressor 201, and is used to detect the suction temperature of the compressor 201; the third temperature sensor 208 is located at the outlet of the compressor 201, and is used to detect the discharge temperature of the compressor 201; the fourth temperature sensor 213 is located around the outdoor heat exchanger 203, and is used to detect the outdoor ambient temperature; the first pressure sensor 211 is located at the inlet of the compressor 201, and is used to detect the suction pressure of the compressor 201; the second pressure sensor 209 is located at the outlet of the compressor 201, and is used to detect the discharge pressure of the compressor 201.

[0029] In some implementations, please refer to Figure 1 Step S03 includes: When the outlet temperature of the indoor heat exchanger 101 is greater than or equal to the suction temperature of the compressor 201, the difference between the outlet temperature of the indoor heat exchanger 101 and the suction temperature of the compressor 201 is determined as the temperature correction amount. When the outlet temperature of the indoor heat exchanger 101 is lower than the suction temperature of the compressor 201, the temperature correction is set to zero.

[0030] In this way, the temperature correction amount can be determined based on the actual temperature changes during the return process, further improving the accuracy of the intake superheat.

[0031] Specifically, when the air conditioning system 100 is in cooling mode, the indoor heat exchanger 101 functions as an evaporator. After heat exchange in the indoor heat exchanger 101, the refrigerant flows from its outlet to the compressor inlet for return gas. During this return gas process, due to the relatively long length of the return gas pipeline connecting the indoor unit 10 and the outdoor unit 20, the refrigerant may experience a temperature drop during its flow due to factors such as pipeline heat dissipation, flow resistance, and the continued evaporation and heat absorption of a small amount of liquid refrigerant. Therefore, by comparing the outlet temperature of the indoor heat exchanger 101 with the suction temperature of the compressor 201, the temperature change of the refrigerant during its journey from the outlet of the indoor heat exchanger 101 to the inlet of the compressor 201 can be observed.

[0032] When the outlet temperature of the indoor heat exchanger 101 is greater than or equal to the suction temperature of the compressor 201, it indicates that the refrigerant temperature decreases during the process of flowing from the outlet of the indoor heat exchanger 101 to the inlet of the compressor 201. Therefore, the difference between the outlet temperature of the indoor heat exchanger 101 and the suction temperature of the compressor 201 is determined as the temperature correction amount, which can compensate for the suction superheat deviation caused by the decrease in refrigerant temperature during the return process.

[0033] When the outlet temperature of the indoor heat exchanger 101 is lower than the suction temperature of the compressor 201, it means that the temperature of the refrigerant has not decreased during the return process. At this time, there is no need to compensate for the suction superheat. Therefore, the temperature correction amount is set to zero, thereby reducing the deviation in the calculation of suction superheat caused by the introduction of additional correction.

[0034] In some implementations, please refer to Figure 1 Step S05 includes: The corresponding saturation temperature is determined based on the suction pressure of compressor 201; The suction superheat is determined based on the suction temperature, saturation temperature, and temperature correction of compressor 201.

[0035] This improves the accuracy of intake superheat calculation.

[0036] Specifically, the suction superheat is usually determined based on the difference between the actual temperature of the refrigerant and the saturation temperature under the actual pressure. The suction pressure of compressor 201 reflects the pressure state of the refrigerant at the compressor 201 inlet, and the corresponding saturation temperature can be obtained from the suction pressure of compressor 201 by looking up tables or other methods.

[0037] Furthermore, since the refrigerant may experience a temperature drop during its flow from the outlet of the indoor heat exchanger 101 to the inlet of the compressor 201 in cooling mode, by introducing a temperature correction amount and combining it with the suction temperature and saturation temperature of the compressor 201 to determine the suction superheat, the impact of the temperature drop during the return process on the suction superheat calculation result can be reduced, thereby improving the accuracy of the suction superheat and providing a more accurate feedback basis for the subsequent opening adjustment of the first valve 102.

[0038] In some implementations, the intake superheat SH satisfies SH = T suc -T esat +k×T corr ; Among them, T suc T represents the suction temperature of compressor 201. esat T represents the saturation temperature. corr This represents the temperature correction amount, and k represents the correction factor.

[0039] Thus, by introducing a correction coefficient to adjust the degree of compensation of the temperature correction amount for the intake superheat, the accuracy of the intake superheat can be further improved.

[0040] Specifically, the correction factor k is used to adjust the degree of influence of the temperature correction in the calculation of suction superheat. By setting different correction factors k, the degree of correction of suction superheat can be adapted to the structural parameters and operating conditions of different air conditioning systems 100.

[0041] In some implementations, the correction factor k can be pre-calibrated based on the actual operating conditions of the air conditioning system 100. For example, the value of the correction factor k can be determined based on factors such as the length of the connecting pipe, the insulation performance of the pipe, and the type of refrigerant, in order to improve the accuracy of the suction superheat.

[0042] In some implementations, the correction factor is 0.25 to 0.8.

[0043] This can improve the accuracy of the inhalation superheat.

[0044] Specifically, the larger the correction factor, the stronger the compensation effect of the temperature correction on the intake superheat; the smaller the correction factor, the weaker the compensation effect of the temperature correction on the intake superheat.

[0045] In practical applications, different air conditioning systems 100 have variations in connecting pipe length, piping layout, insulation performance, and refrigerant circulation state, resulting in varying degrees of temperature change in the refrigerant as it flows from the outlet of the indoor heat exchanger 101 to the inlet of the compressor 201. Therefore, by setting the correction factor to 0.25 to 0.8, the accuracy of the suction superheat can be improved while compensating for the temperature drop during the return gas process.

[0046] In some examples, the correction factor is equal to 0.25, 0.3, 0.35, 0.4, 0.45, 0.5, 0.55, 0.6, 0.65, 0.7, 0.75, 0.8, or other values ​​that are greater than or equal to 0.25 and less than or equal to 0.8.

[0047] In some implementations, please refer to Figure 1 Step S07 includes When the intake superheat is less than the first preset value, the opening of the first valve 102 is reduced; When the intake superheat exceeds the second preset value, the opening of the first valve 102 is increased; When the intake superheat is greater than or equal to the first preset value and less than or equal to the second preset value, the opening of the first valve 102 remains unchanged.

[0048] This can improve the operational stability and energy efficiency of the air conditioning system 100.

[0049] Specifically, when the suction superheat is low, it means that the refrigerant entering the compressor 201 is underheated. At this time, the refrigerant flow rate may be large, and there may be insufficient superheat in the refrigerant at the outlet of the indoor heat exchanger 101. Therefore, by reducing the opening of the first valve 102, the refrigerant flow rate entering the indoor heat exchanger 101 can be reduced, so that the refrigerant has a more complete evaporation process and the suction superheat can be improved.

[0050] When the suction superheat is high, it indicates that the refrigerant entering the compressor 201 is overheated. At this time, the refrigerant supply in the indoor heat exchanger 101 may be insufficient. Therefore, by increasing the opening of the first valve 102, the refrigerant flow rate entering the indoor heat exchanger 101 can be increased, thereby improving the heat exchange capacity of the indoor heat exchanger 101 and reducing the suction superheat.

[0051] When the intake superheat is between the first preset value and the second preset value, it indicates that the current refrigerant flow can meet the operating requirements of the air conditioning system 100. Therefore, the current opening of the first valve 102 is maintained to reduce fluctuations caused by frequent adjustments.

[0052] In some implementations, the first preset value is 2°C to 5°C, and the second preset value is 6°C to 8°C.

[0053] This can improve the stability and energy efficiency of the air conditioning system.

[0054] Specifically, the first preset value and the second preset value are used to limit the control range of the first valve 102. The first preset value is 2°C to 5°C, and the second preset value is 6°C to 8°C. On the one hand, this can avoid the first valve 102 from opening too wide to reduce the risk of liquid refrigerant entering the compressor 201. On the other hand, it can avoid the first valve 102 from opening too small to ensure that the indoor heat exchanger 101 has a sufficient supply of refrigerant, improve the heat exchange capacity of the indoor heat exchanger 101, and thus improve the stability and energy efficiency of the air conditioning system 100.

[0055] In some examples, the first preset value is equal to 2℃, 2.3℃, 2.6℃, 2.9℃, 3.2℃, 3.5℃, 3.8℃, 4.1℃, 4.4℃, 4.7℃, 5℃, or other values ​​that are greater than or equal to 2℃ and less than or equal to 5℃.

[0056] Please see Figure 4 The control device 60 provided in this embodiment of the invention includes a processor 601 and a memory 602. The memory 602 stores a computer program. When the computer program is executed by the processor 601, it implements the control method of any of the above embodiments.

[0057] It should be noted that the above explanation of the implementation method and its beneficial effects also applies to the control device 60 in the embodiments of the present invention. To avoid redundancy, it will not be elaborated in detail here.

[0058] Please see Figures 2 to 4 An air conditioning system 100 provided by an embodiment of the present invention includes an indoor unit 10, an outdoor unit 20 and a control device 60 as described above. The indoor unit 10 includes an indoor heat exchanger 101 and a first valve 102, and the outdoor unit 20 includes an outdoor heat exchanger 203 and a compressor 201. The first valve 102 and the compressor 201 are both electrically connected to the control device 60.

[0059] It should be noted that the above explanation of the implementation method and beneficial effects of the control method also applies to the air conditioning system 100 of the present invention. To avoid redundancy, it will not be elaborated in detail here.

[0060] The present invention provides a computer-readable storage medium storing a computer program thereon, which, when executed by a processor 601, implements the control method of any of the above embodiments.

[0061] In some implementations, when the computer program is executed by the processor 601, the control method includes: Step S03: When the air conditioning system 100 is in cooling mode, determine the temperature correction amount based on the outlet temperature of the indoor heat exchanger 101 and the suction temperature of the compressor 201. Step S05: Determine the suction superheat based on the suction temperature of compressor 201, the suction pressure of compressor 201, and the temperature correction amount. Step S07: Control the opening degree of the first valve 102 according to the superheat of the intake air.

[0062] Computer-readable storage media can be volatile or non-volatile.

[0063] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with an embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0064] Any process or method description in the flowchart or otherwise herein can be understood as representing a module, segment, or box of code comprising one or more steps for implementing a particular logical function or process, and the scope of the preferred embodiments of the invention includes additional implementations in which functions may be performed not in the order shown or discussed, including substantially simultaneously or in reverse order depending on the functions involved, as will be understood by those skilled in the art to which embodiments of the invention pertain.

[0065] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, combinations, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A control method for an air conditioning system, characterized in that, The air conditioning system includes an indoor unit and an outdoor unit. The indoor unit includes an indoor heat exchanger and a first valve. The outdoor unit includes an outdoor heat exchanger and a compressor. The indoor heat exchanger, the first valve, the outdoor heat exchanger, and the compressor are connected by pipelines to form a refrigerant circulation loop. The control method includes: When the air conditioning system is in cooling mode, the temperature correction amount is determined based on the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor. The suction superheat is determined based on the compressor's suction temperature, the compressor's suction pressure, and the temperature correction amount. The opening degree of the first valve is controlled according to the intake superheat.

2. The control method for the air conditioning system according to claim 1, characterized in that, The temperature correction amount is determined based on the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor, including: When the outlet temperature of the indoor heat exchanger is greater than or equal to the suction temperature of the compressor, the difference between the outlet temperature of the indoor heat exchanger and the suction temperature of the compressor is determined as the temperature correction amount. When the outlet temperature of the indoor heat exchanger is lower than the suction temperature of the compressor, the temperature correction amount is determined to be zero.

3. The control method for the air conditioning system according to claim 1, characterized in that, Determining the suction superheat based on the compressor's suction temperature, the compressor's suction pressure, and the temperature correction amount includes: The corresponding saturation temperature is determined based on the suction pressure of the compressor; The suction superheat is determined based on the compressor's suction temperature, the saturation temperature, and the temperature correction amount.

4. The control method for the air conditioning system according to claim 3, characterized in that, The intake superheat SH satisfies SH = T suc -T esat +k×T corr ; Among them, T suc T represents the suction temperature of the compressor. esat T represents the saturation temperature. corr The value represents the temperature correction amount, and k represents the correction coefficient.

5. The control method for an air conditioning system according to claim 4, characterized in that, The correction factor is between 0.25 and 0.

8.

6. The control method for an air conditioning system according to claim 1, characterized in that, Controlling the opening degree of the first valve based on the intake superheat includes When the intake superheat is less than a first preset value, the opening of the first valve is reduced; When the intake superheat is greater than the second preset value, the opening of the first valve is increased; When the intake superheat is greater than or equal to the first preset value and less than or equal to the second preset value, the opening of the first valve remains unchanged.

7. The control method for an air conditioning system according to claim 6, characterized in that, The first preset value is 2°C to 5°C, and the second preset value is 6°C to 8°C.

8. A control device, characterized in that, It includes a processor and a memory, the memory storing a computer program that, when executed by the processor, implements the steps of the control method according to any one of claims 1-7.

9. An air conditioning system, characterized in that, The device includes an indoor unit, an outdoor unit, and the control device described in claim 8. The indoor unit includes an indoor heat exchanger and a first valve, and the outdoor unit includes an outdoor heat exchanger and a compressor. Both the first valve and the compressor are electrically connected to the control device.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by a processor, it implements the steps of the control method according to any one of claims 1-7.

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