CN220471920U

CN220471920U - Air conditioning system

Info

Publication number: CN220471920U
Application number: CN202322115467.8U
Authority: CN
Inventors: 王帆; 金孟孟; 高晗; 滕天凤
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2023-08-07
Filing date: 2023-08-07
Publication date: 2024-02-09
Anticipated expiration: 2033-08-07

Abstract

The present application relates to an air conditioning system. The air conditioning system includes: the indoor unit heat exchanger is used as an evaporator to provide a low-temperature first refrigerant for the multifunctional vapor-liquid separator in a refrigeration mode, is used as a condenser to provide a medium-temperature second refrigerant for the multifunctional vapor-liquid separator in a heating mode, and is used as a condenser to provide a medium-temperature second refrigerant for the multifunctional vapor-liquid separator in a heating mode, namely the indoor unit heat exchanger and the outdoor unit heat exchanger can provide different-temperature refrigerants for the multifunctional vapor-liquid separator in different modes, and the multifunctional vapor-liquid separator can perform heat exchange treatment on the low-temperature first refrigerant provided by the evaporator and the medium-temperature second refrigerant provided by the condenser, so that the supercooling degree of an air conditioning system can be improved.

Description

Air conditioning system

Technical Field

The application relates to the technical field of air conditioners, in particular to an air conditioning system.

Background

In general, when an air conditioner operates, a medium-temperature high-pressure liquid refrigerant flows out from a condensation side, a low-temperature low-pressure gaseous refrigerant flows out from an evaporation side, a large heat exchange temperature difference exists between the two refrigerants, and a better method for exchanging heat for the two refrigerants with large temperature difference is not available in the industry at present, so that the supercooling degree of an air conditioning system cannot be further improved.

Disclosure of Invention

The application provides an air conditioning system to solve current air conditioning system and can't carry out heat exchange to the low-temperature low-pressure gaseous refrigerant that is middle-temperature high-pressure liquid refrigerant and evaporation side outflow that is that the condensation side flows.

The application provides an air conditioning system, comprising:

the indoor unit heat exchanger is used for providing a first refrigerant for the multifunctional vapor-liquid separator as an evaporator in a refrigeration mode, and providing a second refrigerant for the multifunctional vapor-liquid separator as a condenser in a heating mode, wherein the temperature of the first refrigerant is lower than that of the second refrigerant;

the outdoor unit heat exchanger is used as a condenser to provide the second refrigerant for the multifunctional vapor-liquid separator in a refrigeration mode, and used as an evaporator to provide the first refrigerant for the multifunctional vapor-liquid separator in a heating mode;

the multifunctional vapor-liquid separator is respectively communicated with the indoor unit heat exchanger, the outdoor unit heat exchanger, the four-way valve and the compressor, and is used for carrying out heat exchange treatment on the first refrigerant provided by the evaporator and the second refrigerant provided by the condenser and transmitting the gaseous refrigerant subjected to heat exchange to the compressor;

the compressor is respectively communicated with the indoor unit heat exchanger and the outdoor unit heat exchanger through four-way valves and is used for compressing the gaseous refrigerant in a refrigerating mode or a heating mode to realize the refrigeration or heating of the air conditioner;

The indoor unit electronic expansion valve is respectively communicated with the indoor unit heat exchanger and the multifunctional vapor-liquid separator and is used for throttling and depressurizing the second refrigerant into a liquid first refrigerant in a refrigerating mode so that the liquid first refrigerant enters the indoor unit heat exchanger and is evaporated into a gaseous first refrigerant;

and the outdoor unit electronic expansion valve is respectively communicated with the outdoor unit heat exchanger and the multifunctional vapor-liquid separator and is used for throttling and depressurizing the second refrigerant into a liquid first refrigerant in a heating mode so that the liquid first refrigerant enters the outdoor unit heat exchanger and is evaporated into a gaseous first refrigerant.

Optionally, the multifunctional vapor-liquid separator comprises a vapor-liquid separator body and a capillary tube, wherein a pipe inlet of the vapor-liquid separator body is communicated with the four-way valve, a pipe outlet of the vapor-liquid separator body is communicated with the compressor, the capillary tube is arranged at the inner bottom of the vapor-liquid separator body, liquid separating heads are respectively arranged at two ends of the capillary tube, a first end of the capillary tube is communicated with the electronic expansion valve of the indoor unit, a second end of the capillary tube is communicated with a first electromagnetic valve arranged outside the vapor-liquid separator body, and the first electromagnetic valve is also communicated with the electronic expansion valve of the outdoor unit.

Optionally, the air conditioning system further comprises a second electromagnetic valve, wherein the first end of the second electromagnetic valve is respectively communicated with the first electromagnetic valve and the electronic expansion valve of the outdoor unit, and the second end of the electromagnetic valve is respectively communicated with the first end of the capillary tube and the electronic expansion valve of the indoor unit.

Optionally, the outlet pipe orifice and the inlet pipe orifice of the vapor-liquid separator body are respectively provided with a temperature sensor for acquiring the inlet pipe temperature and the outlet pipe temperature of the vapor-liquid separator.

Optionally, the air conditioning system further comprises an enthalpy injection component, and the enthalpy injection component is respectively communicated with the first electromagnetic valve, the second electromagnetic valve, the outdoor unit electronic expansion valve and the compressor and is used for performing enthalpy injection treatment on the compressor.

Optionally, the enthalpy-spraying component comprises a subcooler, a subcooling electronic expansion valve and an enthalpy-spraying electronic expansion valve, the subcooling electronic expansion valve is respectively communicated with the first electromagnetic valve, the second electromagnetic valve and the subcooler, the subcooler is communicated with the outdoor unit heat exchanger through the outdoor unit electronic expansion valve, and the subcooler is also communicated with the compressor through the enthalpy-spraying electronic expansion valve.

Optionally, the air conditioning system further comprises a third electromagnetic valve, wherein the first end of the third electromagnetic valve is respectively communicated with the enthalpy-injection electronic expansion valve and the subcooler, and the second end of the third electromagnetic valve is communicated with the vapor-liquid separator body.

According to the structure provided by the embodiment of the application, the indoor unit heat exchanger is used as the evaporator to provide a low-temperature first refrigerant for the multifunctional vapor-liquid separator in the refrigeration mode, the indoor unit heat exchanger is used as the condenser to provide a medium-temperature second refrigerant for the multifunctional vapor-liquid separator in the heating mode, the outdoor unit heat exchanger is used as the condenser to provide a medium-temperature second refrigerant for the multifunctional vapor-liquid separator in the refrigeration mode, the indoor unit heat exchanger and the outdoor unit heat exchanger can be used as the evaporator to provide low-temperature first refrigerants for the multifunctional vapor-liquid separator in different modes, and the multifunctional vapor-liquid separator can be used for carrying out heat exchange treatment on the low-temperature first refrigerant provided by the evaporator and the medium-temperature second refrigerant provided by the condenser, so that the supercooling degree of an air conditioning system can be improved.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the utility model and together with the description, serve to explain the principles of the utility model.

In order to more clearly illustrate the embodiments of the utility model or the technical solutions of the prior art, the drawings which are used in the description of the embodiments or the prior art will be briefly described, and it will be obvious to a person skilled in the art that other drawings can be obtained from these drawings without inventive effort.

One or more embodiments are illustrated by way of example and not limitation in the figures of the accompanying drawings, in which like references indicate similar elements, and in which the figures of the drawings are not to be taken in a limiting sense, unless otherwise indicated.

FIG. 1 is a schematic diagram of an air conditioning system according to one embodiment;

FIG. 2 is a schematic diagram of an air conditioning system according to one embodiment;

FIG. 3 is a schematic diagram of an air conditioning system according to one embodiment;

FIG. 4 is a schematic diagram of the air conditioning system according to one embodiment;

FIG. 5 is a schematic diagram of the air conditioning system according to one embodiment;

FIG. 6 is a schematic diagram of the air conditioning system according to one embodiment;

FIG. 7 is a flow chart of a method of controlling hollow fiber in accordance with one embodiment;

FIG. 8 is a schematic diagram of a refrigerant cycle corresponding to a first cooling mode in an embodiment;

FIG. 9 is a schematic diagram of a refrigerant cycle corresponding to a second cooling mode in an embodiment;

FIG. 10 is a schematic diagram illustrating a refrigerant cycle corresponding to a third cooling mode in an embodiment;

FIG. 11 is a schematic diagram illustrating a refrigerant cycle corresponding to a first heating mode in an embodiment;

FIG. 12 is a schematic diagram of a refrigerant cycle corresponding to a second heating mode in an embodiment;

FIG. 13 is a schematic diagram illustrating a refrigerant cycle corresponding to a third heating mode in an embodiment;

FIG. 14 is a flow chart of an air conditioning control method in a cooling mode according to an embodiment;

FIG. 15 is a flow chart of an air conditioner control method in a heating mode according to an embodiment;

fig. 16 is a block diagram of an air conditioner control device according to an embodiment of the present application;

fig. 17 is a schematic diagram of an internal structure of a computer device according to an embodiment of the present application.

Detailed Description

For the purposes of making the objects, technical solutions and advantages of the embodiments of the present application more clear, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present application based on the embodiments herein.

The following disclosure provides many different embodiments, or examples, for implementing different structures of the utility model. In order to simplify the present disclosure, components and arrangements of specific examples are described below. They are, of course, merely examples and are not intended to limit the utility model. Furthermore, the present utility model may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed.

FIG. 1 is a schematic diagram of an air conditioning system according to one embodiment. Referring to fig. 1, the air conditioning system includes:

the indoor unit heat exchanger 11 is used as an evaporator to provide a first refrigerant for the multifunctional vapor-liquid separator 13 in a refrigeration mode, and used as a condenser to provide a second refrigerant for the multifunctional vapor-liquid separator 13 in a heating mode, wherein the temperature of the first refrigerant is lower than that of the second refrigerant;

an outdoor heat exchanger 12, configured to serve as a condenser to provide the multifunctional vapor-liquid separator 13 with the second refrigerant in a cooling mode, and serve as an evaporator to provide the multifunctional vapor-liquid separator 13 with the first refrigerant in a heating mode;

The multifunctional vapor-liquid separator 13 is respectively communicated with the indoor unit heat exchanger 11 through an indoor unit electronic expansion valve 24 and the outdoor unit heat exchanger 12 through an outdoor unit electronic expansion valve 22, the four-way valve 14 and the compressor 15, and is used for carrying out heat exchange treatment on the first refrigerant provided by the evaporator and the second refrigerant provided by the condenser and transmitting the gaseous refrigerant after heat exchange to the compressor 15;

the compressor 15 is respectively communicated with the indoor unit heat exchanger 11 and the outdoor unit heat exchanger 12 through a four-way valve 14, and is used for performing different compression treatments on the gaseous refrigerant in a refrigeration mode or a heating mode to release corresponding refrigeration capacity or heating capacity so as to realize refrigeration or heating of an air conditioner;

the indoor unit electronic expansion valve 24 is respectively connected with the indoor unit heat exchanger and the multifunctional vapor-liquid separator, and is used for throttling and depressurizing the second refrigerant into a liquid first refrigerant in a refrigeration mode so that the liquid first refrigerant enters the indoor unit heat exchanger and is evaporated into a gaseous first refrigerant;

and the outdoor unit electronic expansion valve 22 is respectively communicated with the outdoor unit heat exchanger and the multifunctional vapor-liquid separator and is used for throttling and depressurizing the second refrigerant into a liquid first refrigerant in a heating mode so that the liquid first refrigerant enters the outdoor unit heat exchanger and is evaporated into a gaseous first refrigerant.

Specifically, in the refrigeration mode, the compressor 15 provides the third refrigerant to the outdoor heat exchanger 12 through the four-way valve 14, the temperature of the third refrigerant is higher than the temperature of the second refrigerant, namely, the third refrigerant is used for indicating the high-temperature high-pressure gaseous refrigerant, the outdoor heat exchanger 12 is used as a condenser for condensing the third refrigerant discharged from the compressor 15, namely, the third refrigerant is condensed into the second refrigerant, the second refrigerant is used for indicating the medium-temperature high-pressure liquid refrigerant or the medium-temperature high-pressure gas-liquid mixed refrigerant, the second refrigerant of the gas-liquid separator passes through the outdoor machine electronic expansion valve 22 (at the moment, the outdoor machine electronic expansion valve 22 is fully opened without throttling effect, the same applies hereinafter), enters the multifunctional gas-liquid separator 13, and then is throttled and depressurized into the low-temperature low-pressure liquid first refrigerant through the indoor machine electronic expansion valve 24, the refrigerant enters the indoor unit heat exchanger 11, the indoor unit heat exchanger 11 is used as an evaporator to evaporate and convert a low-temperature low-pressure liquid first refrigerant into a low-temperature low-pressure gaseous (or low-temperature low-pressure gas-liquid mixture) first refrigerant, the first refrigerant is used for indicating the low-temperature low-pressure liquid refrigerant or the low-temperature low-pressure gas-liquid mixture refrigerant or the low-temperature low-pressure gaseous refrigerant, the indoor unit heat exchanger 11 evaporates the first refrigerant and then provides the first refrigerant to the multifunctional vapor-liquid separator 13 through the four-way valve, the multifunctional vapor-liquid separator 13 exchanges heat between the first refrigerant provided by the indoor unit heat exchanger 11 and the second refrigerant provided by the outdoor unit heat exchanger 12, and the exchanged low-temperature low-pressure gaseous refrigerant is transmitted back to the compressor 15 for compression treatment so as to complete refrigeration cycle.

In the heating mode, the compressor 15 provides a third refrigerant for the indoor unit heat exchanger 11 through the four-way valve 14, the indoor unit heat exchanger 11 serves as a condenser to condense the third refrigerant into a second refrigerant, the second refrigerant enters the multifunctional vapor-liquid separator 13 through the indoor unit electronic expansion valve 24 (at the moment, the indoor unit electronic expansion valve 24 is fully opened without throttling effect, the same applies below), then the second refrigerant is throttled and depressurized into a low-temperature low-pressure liquid first refrigerant through the outdoor unit electronic expansion valve 22, the low-temperature low-pressure liquid first refrigerant enters the outdoor unit heat exchanger 12, the vapor-liquid separator outdoor unit heat exchanger 12 serves as an evaporator to evaporate and convert the low-temperature low-pressure gaseous first refrigerant into a low-temperature low-pressure gaseous state (or low-temperature low-pressure gaseous-liquid mixture) first refrigerant, then the first refrigerant is transferred back to the multifunctional vapor-liquid separator 13 through the four-way valve 14, the multifunctional vapor-liquid separator 13 exchanges heat between the first refrigerant provided by the outdoor unit heat exchanger 12 and the second refrigerant provided by the indoor unit heat exchanger 11, and the low-temperature low-pressure gaseous refrigerant is transferred back to the compressor 15 to perform compression treatment, and the heating cycle is completed.

In both heating mode and cooling mode, the indoor heat exchanger 11 and the outdoor heat exchanger 12 provide different temperatures for the multifunctional vapor-liquid separator 13, so that the multifunctional vapor-liquid separator 13 not only can perform vapor-liquid separation, but also can exchange heat for the refrigerants with different temperatures provided by the indoor heat exchanger and the outdoor heat exchanger, thereby improving the supercooling degree of the air conditioning system, and when the multifunctional vapor-liquid separator 13 has residual liquid refrigerants, the intermediate temperature refrigerants provided by the indoor heat exchanger or the outdoor heat exchanger can be used for heat exchange to evaporate the residual liquid refrigerants, thereby providing circulating refrigerants for the air conditioning pipeline as much as possible, ensuring that the cooling circulation quantity in the air conditioning pipeline is enough, not affecting the refrigerating or heating effect, reducing the power consumption of the air conditioning system, and improving the energy efficiency of the air conditioning system.

Moreover, because the lubricating oil in the air conditioning system is often stored in the multifunctional vapor-liquid separator 13 together with the low-temperature liquid refrigerant, less lubricating oil returns to the compressor 15, and the compressor 15 may be damaged due to oil shortage and abrasion caused by long-time operation, thereby reducing the operation reliability of the air conditioning system. However, by utilizing the medium-temperature refrigerant provided by the indoor unit heat exchanger or the outdoor unit heat exchanger to evaporate the low-temperature liquid refrigerant stored in the multifunctional vapor-liquid separator 13, lubricating oil fused in the low-temperature liquid refrigerant can be brought back to the compressor 15 through evaporation flow, so that the compressor 15 can not be starved of oil, and the operation reliability of an air conditioning system is improved.

In one embodiment, referring to fig. 2, the multifunctional vapor-liquid separator 13 includes a vapor-liquid separator body 131 and a capillary tube 132, the inlet of the vapor-liquid separator body 131 is communicated with the four-way valve 14, the outlet of the vapor-liquid separator body 131 is communicated with the compressor 15, the capillary tube 132 is disposed at the bottom inside the vapor-liquid separator body 131, two ends of the capillary tube 132 are respectively provided with a liquid separating head 133, a first end of the capillary tube 132 is communicated with the indoor unit heat exchanger 11 through the indoor unit electronic expansion valve 24, a second end of the capillary tube 132 is communicated with a first electromagnetic valve 16 disposed outside the vapor-liquid separator body 131, and the first electromagnetic valve 16 is communicated with the outdoor unit heat exchanger 12 through the outdoor unit electronic expansion valve 22.

Specifically, in the cooling mode, the outdoor heat exchanger 12 transmits the second refrigerant to the capillary tube 132 through the outdoor unit electronic expansion valve 22 and the first electromagnetic valve 16, the capillary tube 132 transmits the second refrigerant to the indoor unit electronic expansion valve 24, the second refrigerant is throttled and depressurized to be a low-temperature low-pressure liquid first refrigerant, then the low-temperature low-pressure liquid first refrigerant enters the indoor heat exchanger 11, the low-temperature low-pressure liquid first refrigerant is evaporated and converted into a low-temperature low-pressure gaseous (or low-temperature low-pressure gas-liquid mixture) first refrigerant in the indoor heat exchanger 11, the first refrigerant is transmitted to the inlet of the vapor-liquid separator body 131 through the four-way valve 14, the first refrigerant, which is located outside the capillary tube 132 and indicates the low-temperature low-pressure gaseous refrigerant or the low-temperature low-pressure gaseous-liquid mixed refrigerant, in the vapor-liquid separator body 131 exchanges heat with the second refrigerant, which is located inside the capillary tube 132 and indicates the medium-temperature high-pressure liquid refrigerant or the medium-temperature high-pressure gaseous-liquid mixed refrigerant, so that the temperature of the second refrigerant can be reduced, the temperature of the first refrigerant can be raised, and the low-temperature liquid refrigerant located outside the capillary tube 132 in the vapor-liquid separator body 131 is subjected to heat exchange and evaporation, so that the low-temperature low-pressure gaseous refrigerant after heat exchange is discharged to the compressor 15 through the outlet of the vapor-liquid separator body 131.

In the heating mode, the indoor heat exchanger 11 transmits the second refrigerant to the capillary tube 132 through the indoor machine electronic expansion valve 24, the capillary tube 132 transmits the second refrigerant to the outdoor machine electronic expansion valve 22 through the first electromagnetic valve 16, so that the second refrigerant is throttled and depressurized to be a low-temperature low-pressure liquid first refrigerant, then the low-temperature low-pressure liquid first refrigerant enters the outdoor machine heat exchanger 12, is evaporated and converted into the low-temperature low-pressure (or low-temperature low-pressure gas-liquid mixed) first refrigerant in the outdoor machine heat exchanger 12, the first refrigerant is transmitted to the inlet of the vapor-liquid separator body 131 through the four-way valve 14, the first refrigerant which is positioned outside the capillary tube 132 and indicates the low-temperature low-pressure gas refrigerant or the low-temperature low-pressure gas-liquid mixed refrigerant in the vapor-liquid separator body 131 is subjected to heat exchange with the second refrigerant which is indicated in the capillary tube 132, the temperature of the second refrigerant can be lowered, the temperature of the first refrigerant is raised, the low-temperature liquid state of the first refrigerant is subjected to heat exchange evaporation of the low-temperature low-pressure liquid state (or low-temperature low-pressure gas-liquid high-pressure liquid refrigerant in the capillary tube 132, and the low-temperature liquid refrigerant is discharged to the vapor-liquid separator body 131 through the outlet of the vapor-liquid separator body 131 to the vapor-pressure separator body 15.

In one embodiment, referring to fig. 3, the inlet and outlet ports of the vapor-liquid separator body 131 are respectively provided at the top of the vapor-liquid separator body 131, and the inlet and outlet ports are respectively provided with a temperature sensor 23 for detecting inlet and outlet pipe temperatures.

In one embodiment, referring to fig. 3, the air conditioning system further includes a second electromagnetic valve 17, wherein a first end of the second electromagnetic valve 17 is respectively connected to the first electromagnetic valve 16 and the outdoor unit electronic expansion valve 22, and a second end of the electromagnetic valve is respectively connected to a first end of the capillary tube 132 and the indoor unit electronic expansion valve 24.

Specifically, when the second electromagnetic valve 17 is closed, the indoor unit heat exchanger 11 or the outdoor unit heat exchanger 12 will transfer all the second refrigerant to the capillary tube 132 through the indoor unit electronic expansion valve 24 or the outdoor unit electronic expansion valve 22 to participate in the heat exchange process, but when the second electromagnetic valve 17 is opened, the indoor unit heat exchanger 11 or the outdoor unit heat exchanger 12 will transfer part of the second refrigerant to the capillary tube 132 through the indoor unit electronic expansion valve 24 or the outdoor unit electronic expansion valve 22 to participate in the heat exchange process, and directly transfer the other part of the second refrigerant to the outdoor unit electronic expansion valve 22 or the indoor unit electronic expansion valve 24 through the second electromagnetic valve 17 after the two parts of the refrigerant are finally converged, and the two parts of the refrigerant enter the outdoor unit heat exchanger 12 or the indoor unit heat exchanger 11 for evaporation after being throttled down to the first refrigerant. Because part of the second refrigerant passes through the second electromagnetic valve 17, the second refrigerant in the capillary tube 132 is less than the second refrigerant when the second electromagnetic valve 17 is closed, so that the second refrigerant participating in heat exchange is reduced, and the temperature difference between the inlet and outlet of the vapor-liquid separator body 131 is prevented from being too large.

The on-off state of the second solenoid valve 17 in the cooling mode is determined by the temperature difference between the inlet and outlet ports of the vapor-liquid separator body 131. If the outdoor environment temperature is less than or equal to the first preset temperature, the second electromagnetic is turned off, the first preset temperature can be set in a personalized mode according to different scenes, and in the embodiment, the first preset temperature is set to be 10 ℃; if the outdoor environment temperature is greater than the first preset temperature and the inlet and outlet pipe temperature difference of the vapor-liquid separator body 131 is less than the preset temperature difference, the second electromagnetic valve 17 is closed, wherein the inlet and outlet pipe temperature difference is the difference between the inlet pipe temperature and the outlet pipe temperature of the vapor-liquid separator body 131, the preset temperature difference can be set individually according to different scenes, and in the embodiment, the preset temperature difference is set to be 5 ℃; if the outdoor ambient temperature is greater than the first preset temperature and the temperature difference between the inlet and outlet pipes of the vapor-liquid separator body 131 is greater than or equal to the first preset temperature, which means that the greater amount of the second refrigerant in the capillary 132 results in greater temperature difference between the inlet and outlet pipes, and the amount of the second refrigerant in the capillary 132 needs to be reduced, the second electromagnetic valve 17 is opened, a portion of the second refrigerant is separated by the second electromagnetic valve 17 to reduce the amount of the second refrigerant in the capillary 132, after the second electromagnetic valve 17 is opened, the temperature difference between the inlet and outlet pipes of the vapor-liquid separator body 131 is still greater than or equal to the first preset temperature according to the first preset period, which means that the amount of the second refrigerant in the capillary 132 is still greater, the first electromagnetic valve 16 is closed, that is, the second refrigerant is not provided for the capillary 132 any more, all the second refrigerant is directly transferred from the outdoor unit heat exchanger 12 to the indoor unit electronic expansion valve 24 through the second electromagnetic valve 17, and is throttled down to the first refrigerant through the indoor unit electronic expansion valve 24, and then enters the indoor unit heat exchanger 11 for evaporation. The first preset period may be any duration, and in this embodiment, the first preset period is made to be 10 minutes.

During the heating operation of the air conditioning system in winter, the outdoor heat exchanger 12 often operates for a period of time and then frosts, so that the on-off state of the second electromagnetic valve 17 in the heating mode is determined by the number of frosting times of the outdoor heat exchanger 12 in a preset period. If the outdoor ambient temperature is less than or equal to the second preset temperature, the second preset temperature may be set individually according to different scenes, in this embodiment, the second preset temperature is set to-5 ℃, which belongs to low-temperature heating, at this time, the vapor contained in the air is less, the heat exchanger 12 of the outdoor unit will not frost basically, the second electromagnetic valve 17 is closed, the second refrigerant is transferred only through the first electromagnetic valve 16 and the capillary tube 132, the second refrigerant (medium-temperature liquid refrigerant) in the capillary tube 132 exchanges heat with the first refrigerant (low-temperature gaseous refrigerant or low-temperature liquid refrigerant or low-temperature gas-liquid mixed refrigerant) outside the capillary tube 132, the supercooling degree is improved, the suction temperature and suction superheat degree of the compressor 15 are improved, if the liquid refrigerant exists in the vapor-liquid separator body 131, the heat exchange evaporation can be performed, the liquid refrigerant in the vapor-liquid separator body 131 is reduced, and the lubricating oil melted in the liquid refrigerant is brought back to the compressor 15 through evaporation flow, so as to ensure that the compressor 15 will not be in oil-starved operation, or the refrigerant will be stored in the vapor-liquid separator when the outdoor ambient temperature is too low as-temperature is below-30 ℃, or when the air conditioning system is in low-load operation, or when the vapor-liquid refrigerant is in the outdoor heat exchanger 12 is in the vapor-liquid separator.

If the outdoor ambient temperature is greater than the second preset temperature and the defrosting frequency of the outdoor heat exchanger 12 in the third preset period is less than the preset frequency, closing the second electromagnetic valve 17; if the outdoor ambient temperature is greater than the second preset temperature and the number of defrosting times of the outdoor heat exchanger 12 in the third preset period is greater than or equal to the preset number of times, which means that the number of defrosting times of the outdoor heat exchanger 12 is greater, the temperature of the second refrigerant provided to the outdoor electronic expansion valve 22 needs to be increased in order to reduce the number of defrosting times, the second electromagnetic valve 17 is opened, and a part of the second refrigerant is separated by the second electromagnetic valve 17, namely, the refrigerant quantity of the second refrigerant participating in heat exchange in the capillary tube 132 is reduced, so that the temperature of the second refrigerant transmitted to the outdoor electronic expansion valve 22 can be increased; after the second electromagnetic valve 17 is opened, the defrosting frequency of the outdoor unit heat exchanger 12 in the third preset period is still greater than or equal to the preset frequency, which means that the temperature of the second refrigerant received by the outdoor unit electronic expansion valve 22 is still lower, the temperature is too low after the second refrigerant is throttled and depressurized to the first refrigerant through the outdoor unit electronic expansion valve 22, and is easy to frost, the first electromagnetic valve 16 is closed, the second refrigerant for inhibiting the capillary tube 132 from providing heat exchange is directly transmitted to the outdoor unit electronic expansion valve 22 from the indoor unit electronic expansion valve 24 through the second electromagnetic valve 17, and the second refrigerant is throttled and depressurized through the outdoor unit electronic expansion valve 22 and then enters the outdoor unit heat exchanger 12, at the moment, the temperature of the first refrigerant is higher than the previous temperature, so that the defrosting frequency can be reduced. The preset period may be a period corresponding to any time length, in this embodiment, the third preset period is set to 2 hours, the preset number of times may be any number, and in this embodiment, the preset number of times is set to 3.

In one embodiment, the air conditioning system further includes an enthalpy injection assembly, which is respectively connected to the first solenoid valve 16, the second solenoid valve 17, the outdoor unit electronic expansion valve 22, and the compressor 15, for performing an enthalpy injection treatment on the air conditioning system.

Specifically, the principle of enthalpy injection is to throttle and decompress the second refrigerant into the first refrigerant through the electronic expansion valve 18 of the subcooler, exchange heat with the second refrigerant in the subcooler 17, reduce the temperature of the second refrigerant, and spray the first refrigerant into the compressor after the first refrigerant absorbs heat and flows out of the subcooler, so as to increase the exhaust enthalpy value of the compressor.

In one embodiment, referring to fig. 4, the enthalpy injection assembly includes a subcooler 107, a subcooling electronic expansion valve 18, and an enthalpy injection electronic expansion valve 19, wherein the subcooling electronic expansion valve 18 is respectively in communication with the first solenoid valve 16, the second solenoid valve 17, and the subcooler 107, the subcooler 107 is in communication with the outdoor heat exchanger 12 through an outdoor electronic expansion valve 22, and the subcooler 107 is also in communication with the compressor 15 through the enthalpy injection electronic expansion valve 19.

Specifically, when the air conditioning system needs to spray enthalpy, the second refrigerant is throttled and depressurized by the supercooling electronic expansion valve 18 to be a low-temperature low-pressure gaseous state or a low-temperature low-pressure gas-liquid mixed first refrigerant, then exchanges heat with the second refrigerant in the supercooler 107 to reduce the temperature of the second refrigerant, and the first refrigerant flows out of the supercooler 107 and then enters the compressor 15 through the enthalpy-spraying electronic expansion valve 19 to perform the air injection enthalpy-increasing treatment on the air conditioning system, so that the refrigerating capacity or the heating capacity is improved.

In one embodiment, referring to fig. 5, the air conditioning system further includes a third solenoid valve 20, a first end of the third solenoid valve 20 is respectively connected to the electronic vapor injection expansion valve 19 and the subcooler 107, and a second end of the third solenoid valve 20 is connected to the vapor-liquid separator body 131.

Specifically, when the air conditioning system does not open the enthalpy and only opens the subcooling, the electronic expansion valve 19 is closed, the third electromagnetic valve 20 is opened, and the first refrigerant output by the subcooler is transferred to the vapor-liquid separator body 131 through the third electromagnetic valve 20.

In one embodiment, an oil separator 21 is further provided between the compressor 15 and the four-way valve 14 as described with reference to fig. 6. The oil separator 21 can separate out the lubricating oil in the refrigerant and return the lubricating oil to the compressor 15, so that the phenomenon that the lubricating oil in the compressor 15 gradually enters a refrigerant circulation pipeline to cause the oil shortage of the compressor 15 is avoided, and the operation reliability of an air conditioning system can be improved.

In one embodiment, fig. 7 is a schematic flow chart of an air conditioner control method in one embodiment, and referring to fig. 7, an air conditioner control method is provided. The embodiment is mainly exemplified by the application of the method to an air conditioner control device, and the air conditioner control method specifically comprises the following steps:

Step S210, acquiring outdoor environment temperature and air-conditioning operation parameters of an air-conditioning system, wherein the air-conditioning system comprises a multifunctional vapor-liquid separator 13, an evaporator, a condenser, a four-way valve, an electronic expansion valve and a compressor.

Specifically, the air conditioning system includes an indoor heat exchanger 11, an outdoor heat exchanger 12, a four-way valve 14, an outdoor electronic expansion valve 22, an indoor electronic expansion valve 24, and a compressor 15. In the cooling mode, the indoor heat exchanger 11 serves as an evaporator, the outdoor heat exchanger 12 serves as a condenser, and in the heating mode, the outdoor heat exchanger 12 serves as an evaporator, and the indoor heat exchanger 11 serves as a condenser. The air-conditioning operation parameters include the current operation mode of the air-conditioning system, the temperature difference of the inlet pipe and the outlet pipe of the multifunctional vapor-liquid separator 13, the defrosting times and the like.

And step S220, determining a target operation mode according to the outdoor environment temperature and the air conditioner operation parameters.

Specifically, according to the outdoor ambient temperature, it is possible to determine which of low-temperature refrigeration, low-temperature heating, high-temperature refrigeration, high-temperature heating, and the like the operation state of the air conditioning system is, and further determine a target operation mode for controlling the operation of the air conditioning system by combining with the operation parameters of the air conditioning system, where the target operation mode includes a refrigeration mode and a heating mode, the refrigeration mode includes a first refrigeration mode, a second refrigeration mode, and a third refrigeration mode, the heating mode includes a first heating mode, a second heating mode, and a third heating mode, and the air intake temperatures provided for the compressor 15 in different refrigeration modes are different, and the refrigerant temperatures provided for the outdoor heat exchanger 12 in different heating modes are different.

And step S230, when the target operation mode is a preset heat exchange mode, controlling the multifunctional vapor-liquid separator 13 to perform heat exchange treatment on a first refrigerant provided by the evaporator and a second refrigerant provided by the condenser, wherein the temperature of the first refrigerant is lower than that of the second refrigerant.

Specifically, the preset heat exchange mode is any one of a first refrigeration mode, a second refrigeration mode, a first heating mode and a second heating mode, and when the target operation mode is the preset heat exchange mode, the multifunctional vapor-liquid separator 13 is controlled to perform heat exchange treatment on a first refrigerant provided by the evaporator and a second refrigerant provided by the condenser, wherein the first refrigerant is used for indicating a low-temperature low-pressure liquid refrigerant or a low-temperature low-pressure gas-liquid mixed refrigerant, and the second refrigerant is used for indicating a medium-temperature high-pressure liquid refrigerant or a medium-temperature high-pressure gas-liquid mixed refrigerant. The heat exchange is carried out on the low-temperature first refrigerant and the medium-temperature second refrigerant, so that the supercooling degree of the air conditioning system can be improved.

In one embodiment, the determining the target operation mode according to the outdoor environment temperature and the air conditioner operation parameter includes:

when the current operation mode in the air conditioner operation parameters is a refrigeration mode and the outdoor environment temperature is less than or equal to a first preset temperature, determining a first refrigeration mode as the target operation mode, wherein the multifunctional vapor-liquid separator performs heat exchange treatment with the first refrigerant by using all the second refrigerants in the first refrigeration mode; or alternatively, the first and second heat exchangers may be,

When the outdoor environment temperature is higher than a first preset temperature, determining the first refrigeration mode as the target operation mode, and judging whether a first inlet and outlet pipe temperature difference of the multifunctional vapor-liquid separator 13 in the air conditioner operation parameters is lower than a preset temperature difference or not according to a first preset period;

and when the temperature difference of the first inlet and outlet pipes is smaller than the preset temperature difference, the first refrigeration mode is kept as the target operation mode.

Specifically, the current operation mode of the air conditioning system is a refrigeration mode, which means that the air conditioning system is currently refrigerating, and then it is determined whether the outdoor environmental temperature is greater than a first preset temperature, the outdoor environmental temperature is denoted as T, the first preset temperature is denoted as T3, and if the outdoor environmental temperature is less than or equal to the first preset temperature, that is, T is less than or equal to T3, the first refrigeration mode is determined as a target operation mode, and referring to fig. 8, the operation process of the air conditioning system in the first refrigeration mode is as follows: the refrigerant sequentially passes through the compressor 15, the oil separator 21, the four-way valve 14, the outdoor unit heat exchanger 12, the outdoor unit electronic expansion valve 22, the subcooler 107, the first electromagnetic valve 16, the capillary tube 132 of the multifunctional vapor-liquid separator 13, the indoor unit electronic expansion valve 24, the indoor unit heat exchanger 11, the four-way valve 14, the inlet pipe orifice of the multifunctional vapor-liquid separator 13, the outlet pipe orifice of the multifunctional vapor-liquid separator 13 and the compressor 15 to complete refrigerant circulation.

The outdoor heat exchanger 12 serves as a condenser to provide a medium-temperature high-pressure second refrigerant for the capillary tube 132 in the multifunctional vapor-liquid separator 13, the indoor heat exchanger 11 provides a low-temperature low-pressure first refrigerant for the multifunctional vapor-liquid separator 13 through the four-way valve 14, and the multifunctional vapor-liquid separator 13 can serve as a heat exchanger to perform heat exchange treatment on the first refrigerant and the second refrigerant at the moment and transfer the gaseous refrigerant after heat exchange back to the compressor 15.

When the outdoor environment temperature T is less than or equal to T3 for refrigeration, the outdoor environment temperature T is low-temperature refrigeration, and there may be a situation that a liquid refrigerant exists in the multifunctional vapor-liquid separator 13, for example, the indoor temperature is set to be too low at-5 ℃, or the low-load operation of the air conditioning system may cause the liquid refrigerant to exist in the multifunctional vapor-liquid separator 13, the situation is default to operate according to the first refrigeration mode, at this time, the capillary tube 132 of the multifunctional vapor-liquid separator 13 is a medium-temperature liquid second refrigerant, the medium-temperature liquid refrigerant is the second refrigerant, the outside of the capillary tube 132 is a low-temperature gaseous or liquid or gas-liquid mixed first refrigerant, that is, the first refrigerant is the low-temperature gaseous or liquid refrigerant, the inside and outside of the capillary tube 132 exchanges heat, the temperature of the medium-temperature liquid refrigerant in the capillary tube 132 is reduced, and then the medium-temperature liquid refrigerant is throttled and depressurized to the low-temperature low-pressure liquid first refrigerant by the indoor unit electronic expansion valve 24, and then enters the indoor unit heat exchanger 11 for evaporation treatment, thereby the supercooling degree of the air conditioning system is improved, and the suction temperature and the suction superheat degree of the compressor 15 can be improved. If the liquid refrigerant exists, the liquid refrigerant can be evaporated, and the lubricating oil fused in the liquid refrigerant is brought back to the compressor 15 through evaporation flow, so that an oil return effect is realized, the compressor 15 is ensured not to run in a shortage of oil, and the running reliability of an air conditioning system is improved.

If the outdoor ambient temperature is greater than a first preset temperature, i.e., T > T3, the air conditioning system is controlled to operate according to the first refrigeration mode, and whether the first inlet and outlet pipe temperature difference of the multifunctional vapor-liquid separator 13 is smaller than the preset temperature difference is determined at regular time according to the first preset period, the inlet and outlet pipe temperature difference is a difference between the inlet pipe temperature and the outlet pipe temperature of the vapor-liquid separator body 131, T1 is used for indicating the inlet pipe temperature, T2 is used for indicating the outlet pipe temperature, Δt=5 ℃ is combined with the above embodiment, i.e., whether T1-T2 < "Δt" is established, and if so, operation according to the first refrigeration mode is continued.

In one embodiment, after determining the first cooling mode as the target operation mode when the outdoor ambient temperature is greater than a first preset temperature and determining whether a first inlet and outlet pipe temperature difference of the multifunctional vapor-liquid separator 13 in the air conditioner operation parameters is less than a preset temperature difference according to a first preset period, the method further includes:

when the first inlet and outlet pipe temperature difference is greater than or equal to the preset temperature difference, switching the target operation mode from the first refrigeration mode to a second refrigeration mode, and judging whether the second inlet and outlet pipe temperature difference of the multifunctional vapor-liquid separator 13 in the air conditioner operation parameters is smaller than the preset temperature difference according to a second preset period at regular time;

When the second inlet and outlet pipe temperature difference is smaller than the preset temperature difference, the second refrigeration mode is kept as the target operation mode; or alternatively, the first and second heat exchangers may be,

and when the temperature difference of the second inlet and outlet pipes is greater than or equal to the preset temperature difference, switching the target operation mode from the second refrigeration mode to a third refrigeration mode, wherein the multifunctional vapor-liquid separator 13 does not perform heat exchange treatment on the second refrigerant and the first refrigerant in the third refrigeration mode.

Specifically, referring to fig. 9, the air conditioning system operates in the second cooling mode as follows: refrigerant passes through the compressor 15, the oil separator 21, the four-way valve 14, the outdoor unit heat exchanger 12, the outdoor unit electronic expansion valve 22, the subcooler 107, the second electromagnetic valve 17, the (the capillary tube 132 of the first electromagnetic valve 16+the multifunctional vapor-liquid separator 13), the indoor unit electronic expansion valve 24, the indoor unit heat exchanger 11, the four-way valve 14, the inlet pipe orifice of the multifunctional vapor-liquid separator 13, the outlet pipe orifice of the multifunctional vapor-liquid separator 13 and the compressor 15 in sequence, and completes refrigerant circulation.

Referring to fig. 10, the air conditioning system operates in the third cooling mode as follows: the refrigerant sequentially passes through the compressor 15, the oil separator 21, the four-way valve 14, the outdoor unit heat exchanger 12, the outdoor unit electronic expansion valve 22, the subcooler 107, the second electromagnetic valve 17, the indoor unit electronic expansion valve 24, the indoor unit heat exchanger 11, the four-way valve 14, the inlet pipe orifice of the multifunctional vapor-liquid separator 13, the outlet pipe orifice of the multifunctional vapor-liquid separator 13 and the compressor 15, so that the refrigerant circulation is completed.

When T1-T2 is greater than or equal to Δt, it is indicated that the excessive temperature difference between the inlet pipe temperature and the outlet pipe temperature of the capillary tube 132 causes the excessive temperature difference between the inlet pipe temperature and the outlet pipe temperature of the multifunctional vapor-liquid separator 13, and at this time, the second solenoid valve 17 is switched from the first refrigeration mode to the second refrigeration mode, that is, the second solenoid valve 17 is opened, a part of the medium-temperature liquid refrigerant bypasses the pipeline where the second solenoid valve 17 is located, and then joins the medium-temperature liquid refrigerant passing through the capillary tube 132 and then transfers the same to the indoor unit electronic expansion valve 24, and the medium-temperature liquid refrigerant is throttled and depressurized by the indoor unit electronic expansion valve 24 to be transferred to the indoor unit heat exchanger 11, so that the difference Δt between the inlet pipe temperature T1 and the outlet pipe temperature T2 can be reduced, so that the difference Δt between the inlet pipe temperature T1 and the outlet pipe temperature T2 is equal to or different from the first preset period, that in this embodiment, that the second preset period is equal to the first preset period, that is 10 minutes. If the air conditioning system still detects T1-T2 is more than or equal to DeltaT after operating according to the second refrigeration mode for 10 minutes, which indicates that the medium-temperature liquid refrigerant in the capillary tube 132 is still excessive, the air conditioning system is switched from the second refrigeration mode to the third refrigeration mode, namely, the first electromagnetic valve 16 is closed, the second electromagnetic valve 17 is only opened, the medium-temperature liquid refrigerant does not enter the capillary tube 132 in the vapor-liquid separator any more, all the medium-temperature liquid refrigerant is transmitted to the indoor unit electronic expansion valve 24 through the second electromagnetic valve 17, is throttled and depressurized to be the first refrigerant through the indoor unit electronic expansion valve 24 and then is transmitted to the indoor unit heat exchanger 11, and the air conditioning system resumes operation according to the first refrigeration mode again after being shut down and restarted.

In one embodiment, when the target operation mode is a preset heat exchange mode, the controlling the multifunctional vapor-liquid separator 13 to perform heat exchange processing on the first refrigerant provided by the evaporator and the second refrigerant provided by the condenser includes:

when the target operation mode is the first refrigeration mode or the second refrigeration mode, the multifunctional vapor-liquid separator 13 is controlled to perform heat exchange treatment on the first refrigerant provided by the indoor unit heat exchanger 11 and the second refrigerant provided by the outdoor unit heat exchanger 12, wherein the preset heat exchange mode is the first refrigeration mode or the second refrigeration mode, the indoor unit heat exchanger 11 in the air conditioning system is used as an evaporator in the refrigeration mode, and the outdoor unit heat exchanger 12 in the air conditioning system is used as a condenser in the refrigeration mode.

Specifically, in combination with the above embodiment, the preset heat exchange mode is the first refrigeration mode or the second refrigeration mode, and the multifunctional vapor-liquid separator 13 only can perform the vapor-liquid separation function in the third refrigeration mode, and cannot perform the heat exchange function of the heat exchanger.

When the current operation mode in the air conditioner operation parameters is a heating mode and the outdoor environment temperature is less than or equal to a second preset temperature, determining a first heating mode as the target operation mode, wherein the multifunctional vapor-liquid separator performs heat exchange treatment with the first refrigerant by using all the second refrigerants in the first heating mode; or alternatively, the first and second heat exchangers may be,

when the outdoor environment temperature is higher than a second preset temperature, determining the first heating mode as the target operation mode, and judging whether the first defrosting times in a third preset period are lower than preset times or not according to the third preset period at regular time, wherein the air conditioner operation parameters further comprise the first defrosting times;

and when the first defrosting times are smaller than the preset times, the first heating mode is kept as the target operation mode.

Specifically, when the air conditioning system heats, it is determined whether the outdoor ambient temperature is greater than a second preset temperature, and the second preset temperature is recorded as T4, that is, whether T > T4 is satisfied, and by combining the above embodiments, it is known that the second preset temperature is-5 ℃, that is, t4= -5 ℃. If T is less than or equal to T4, the air is heated at a low temperature, and the water vapor contained in the air is less under the condition, the air conditioning system basically does not frost when in operation, namely, the lower the outdoor ambient temperature is, the less frosting is caused, and the multifunctional vapor-liquid separator 13 possibly stores liquid refrigerant when the air conditioning system is in operation, so that the medium-temperature liquid refrigerant in the capillary tube 132 and the low-temperature gaseous or liquid or gas-liquid mixed refrigerant outside the capillary tube 132 are subjected to heat exchange by adopting a first heating mode, the supercooling degree is improved, and the air suction temperature and the air suction superheat degree of the compressor are improved. If the liquid refrigerant exists, the liquid refrigerant can be evaporated, and the lubricating oil melted in the liquid refrigerant is brought back to the compressor 15 through evaporation flow, so that the oil return effect of the compressor 15 is realized.

When the outdoor environment temperature T is greater than T4, the air conditioner is easy to frost during operation, particularly when the outdoor environment temperature is within the range of-5 ℃ to 5 ℃, the outdoor heat exchanger 12 is frequently frosted and defrosted, the air conditioner is operated according to the first heating mode, at this time, all the second refrigerants enter the capillary tube 132 of the multifunctional gas-liquid separator, after the air conditioner is operated according to the first heating mode, the defrosting times are collected at regular time according to the third preset period, the preset times are 3, the third preset period is t5=2h, and if the defrosting times are detected for N <3 times in the third preset period, the operation of the first heating mode can be maintained if the defrosting times of the outdoor heat exchanger 12 are less.

Referring to fig. 11, the air conditioning system operates in the first heating mode as follows: the refrigerant sequentially passes through the compressor 15, the oil separator 21, the four-way valve 14, the indoor unit heat exchanger 11, the indoor unit electronic expansion valve 24, the capillary tube 132 of the multifunctional vapor-liquid separator 13, the first electromagnetic valve 16, the subcooler 107, the outdoor unit electronic expansion valve 22, the outdoor unit heat exchanger 12, the four-way valve 14, the inlet pipe orifice of the multifunctional vapor-liquid separator 13, the outlet pipe orifice of the multifunctional vapor-liquid separator 13 and the compressor 15 to complete refrigerant circulation.

In one embodiment, when the outdoor ambient temperature is greater than a second preset temperature, determining the first heating mode as the target operation mode, and determining, according to a third preset period, whether the first defrosting number in the third preset period is less than a preset number, where after the first heating mode is determined, the method further includes:

When the first defrosting times are greater than or equal to the preset times, switching the target operation mode from the first heating mode to a second heating mode, and judging whether the second defrosting times in a fourth preset period are smaller than the preset times or not according to the fourth preset period at regular time, wherein the multifunctional vapor-liquid separator utilizes part of the second refrigerant and the first refrigerant to perform heat exchange treatment under the second heating mode;

when the second defrosting times are smaller than the preset times, the second heating mode is kept as the target operation mode; or alternatively, the first and second heat exchangers may be,

and when the second defrosting times are greater than or equal to the preset times, switching the target operation mode from the second heating mode to a third heating mode, wherein the multifunctional vapor-liquid separator does not perform heat exchange treatment on the second refrigerant and the first refrigerant in the third heating mode.

Specifically, if the number of defrosting times N is greater than or equal to 3 in the third preset period, which indicates that defrosting is too frequent, at this time, the first heating mode is switched to the second heating mode, that is, the second electromagnetic valve 17 is opened, a part of the medium-temperature liquid refrigerant passes through the second electromagnetic valve 17 and then flows into the outdoor unit electronic expansion valve 22 after being converged with the liquid refrigerant flowing out of the low-temperature first electromagnetic valve 16 of the vapor-liquid separator, and enters the outdoor unit heat exchanger 12 for evaporation and heat absorption after being throttled and depressurized into the first refrigerant by the outdoor unit electronic expansion valve 22. The refrigerant passing through the second electromagnetic valve 17 does not exchange heat, so after merging with the refrigerant flowing out of the first electromagnetic valve 16, the temperature of the refrigerant passing through the first electromagnetic valve 16 is higher than that of the refrigerant in the medium temperature liquid state in the first heating mode, and the temperature of the refrigerant throttled by the outdoor unit electronic expansion valve 22 is also higher, and the supercooling degree is reduced, so that the frosting times of the outdoor unit heat exchanger 12 can be reduced, if the frosting times N <3 times in the third preset period T5 are continuously detected, the fact that the frosting times of the outdoor unit heat exchanger 12 in the corresponding period of the third preset period are less is indicated, and the second heating mode operation can be continuously maintained.

If the defrosting times N in the third preset period T5 are continuously detected to be more than or equal to 3 times, the operation is switched from the second heating mode to the third heating mode, namely, the first electromagnetic valve 16 is closed, only the second electromagnetic valve 17 is opened, the medium-temperature liquid refrigerant flowing out of the indoor unit heat exchanger 11 does not flow into the vapor-liquid separator any more, and the medium-temperature liquid refrigerant is directly throttled and depressurized into the first refrigerant through the second electromagnetic valve 17 and the outdoor unit electronic expansion valve 22 in sequence and then flows into the outdoor unit heat exchanger 12.

When the outdoor environment temperature of the air conditioning system is higher than the first preset temperature, for example, the outdoor environment temperature is about 15 ℃, the outdoor heat exchanger 12 is not frosted, and the first heating mode is adopted to operate at the moment, so that the supercooling degree of the air conditioning system can be improved, the air suction temperature of the compressor 15 can be increased, the air discharge temperature of the compressor 15 can be increased, the air conditioning heating amount can be increased, and the air conditioning energy efficiency can be improved. That is, when T < -5 ℃ or T > 15 ℃, the first heating mode is adopted under the condition that the air conditioner does not frost, the supercooling degree and the air suction temperature of the compressor 15 can be improved, the heating quantity is increased, and when T is within-5 ℃ to 5 ℃, T is the environment temperature which is easy to frost, the frosting frequency of the outdoor unit heat exchanger 12 (which is used as an evaporator at the moment) is directly influenced by the supercooling degree, so the heating mode needs to be adjusted according to the method.

Referring to fig. 12, the air conditioning system operates in the second heating mode as follows: the refrigerant sequentially passes through the compressor 15, the oil separator 21, the four-way valve 14, the indoor unit heat exchanger 11, the indoor unit electronic expansion valve 24, the second electromagnetic valve 17, the capillary tube 132 of the (first electromagnetic valve 16+the multifunctional vapor-liquid separator 13), the subcooler 107, the outdoor unit electronic expansion valve 22, the outdoor unit heat exchanger 12, the four-way valve 14, the inlet pipe orifice of the multifunctional vapor-liquid separator 13, the outlet pipe orifice of the multifunctional vapor-liquid separator 13 and the compressor 15, and the refrigerant circulation is completed.

Referring to fig. 13, the air conditioning system operates in the third heating mode as follows: the refrigerant sequentially passes through the compressor 15, the oil separator 21, the four-way valve 14, the indoor unit heat exchanger 11, the indoor unit electronic expansion valve 24, the second electromagnetic valve 17, the subcooler 107, the outdoor unit electronic expansion valve 22, the outdoor unit heat exchanger 12, the four-way valve 14, the inlet pipe orifice of the multifunctional vapor-liquid separator 13, the outlet pipe orifice of the multifunctional vapor-liquid separator 13 and the compressor 15, so that the refrigerant circulation is completed.

When the target operation mode is the first heating mode or the second heating mode, the multifunctional vapor-liquid separator 13 is controlled to perform heat exchange treatment on the first refrigerant provided by the outdoor unit heat exchanger 12 and the second refrigerant provided by the indoor unit heat exchanger 11, wherein the preset heat exchange mode is the first heating mode or the second heating mode, the outdoor unit heat exchanger 12 in the air conditioning system is used as an evaporator in the heating mode, and the indoor unit heat exchanger 11 in the air conditioning system is used as a condenser in the heating mode.

Specifically, in combination with the above embodiment, the preset heat exchange mode is a first heating mode or a second heating mode, and the multifunctional vapor-liquid separator 13 only has the function of vapor-liquid separation in the third heating mode, but cannot have the heat exchange function of the heat exchanger.

In one particular embodiment, referring to fig. 14, the air conditioning system is in cooling operation:

if T is less than or equal to t3=10deg.C, the air conditioner maintains the operation of the refrigeration mode 1 (i.e. the first refrigeration mode);

if T is more than T3=10deg.C, the air conditioner is operated in a default refrigeration mode 1 after being started, and then detecting whether T1-T2 is more than or equal to DeltaT=5deg.C every 10 minutes;

if T1-T2 < DeltaT=5 ℃, maintaining the refrigeration mode 1 to operate, and continuously detecting whether T1-T2 is more than or equal to DeltaT=5 ℃ every 10 minutes;

If T1-t2 is not less than Δt=5 ℃, switching from cooling mode 1 to cooling mode 2 (i.e., being a second cooling mode), at which time the second solenoid valve 17 is opened, and then detecting whether T1-t2 is not less than Δt=5 ℃ every 10 minutes;

if T1-T2 < DeltaT=5 ℃, keeping the refrigeration mode 2 to continue to operate, and continuously detecting whether T1-T2 is more than or equal to DeltaT=5 ℃ every 10 minutes;

if T1-t2 is not less than Δt=5 ℃, the mode is switched from cooling mode 2 to cooling mode 3 (i.e., the third cooling mode), and at this time, the first solenoid valve 16 is closed, and only the second solenoid valve 17 is opened, until the air conditioner is restarted after being shut down, and returns to cooling mode 1.

Referring to fig. 15, the air conditioning system is in heating operation:

if T is less than or equal to T4= -5 ℃, the air conditioner keeps the heating mode 1 (namely the first heating mode) to operate;

if T is more than T4= -5 ℃, the default heating mode 1 operates after the air conditioner is started, and then whether the defrosting times N of the air conditioner in the time period is more than or equal to 3 is detected once every T5=2h;

if N is less than 3, maintaining the operation of the heating mode 1, and continuously detecting whether the defrosting times N of the air conditioner in the time period is more than or equal to 3 every T5=2h;

if N is greater than or equal to 3, switching from the heating mode 1 to the heating mode 2 (i.e., the second heating mode), opening the second electromagnetic valve 17 at this time, and continuously detecting whether the defrosting frequency N of the air conditioner in the time period is greater than or equal to 3 once every t5=2h;

If N is less than 3, maintaining the heating mode 2 to continue to operate, and continuously detecting whether the defrosting times N of the air conditioner in the time period is more than or equal to 3 every T5=2h;

if N is more than or equal to 3, the heating mode is switched from the heating mode 2 to the heating mode 3 (namely, the third heating mode), at the moment, the first electromagnetic valve 16 is closed, and only the second electromagnetic valve 17 is opened until the air conditioner is restarted after being shut down, and the air conditioner is restored to the heating mode 1.

When the air conditioning system needs to spray enthalpy, the refrigerant sequentially passes through the supercooling electronic expansion valve 18, the supercooler 107 and the enthalpy-spraying electronic expansion valve 19 to enter the compressor 15; if the air conditioner only needs supercooling, the enthalpy injection electronic expansion valve 19 is closed, the third electromagnetic valve 20 is opened, and the refrigerant enters the multifunctional vapor-liquid separator 13 through the third electromagnetic valve 20.

Fig. 7, 14, 15 are flow diagrams of a hollow-core control method according to an embodiment. It should be understood that, although the steps in the flowcharts of fig. 7, 14, 15 are shown in order as indicated by the arrows, these steps are not necessarily performed in order as indicated by the arrows. The steps are not strictly limited to the order of execution unless explicitly recited herein, and the steps may be executed in other orders. Moreover, at least some of the steps of fig. 7, 14, 15 may comprise a plurality of sub-steps or phases, which are not necessarily performed at the same time, but may be performed at different times, nor does the order of execution of the sub-steps or phases necessarily follow one another, but may be performed alternately or alternately with at least some of the other steps or sub-steps of other steps.

In one embodiment, as shown in fig. 16, there is provided an air conditioner control device including:

an acquisition module 310 for acquiring an outdoor environment temperature and an air conditioner operation parameter;

a determining module 320, configured to determine a target operation mode according to the outdoor environment temperature and the air-conditioning operation parameter;

and the control module 330 is configured to control the multifunctional vapor-liquid separator 13 to perform heat exchange treatment on a first refrigerant provided by the evaporator and a second refrigerant provided by the condenser when the target operation mode is a preset heat exchange mode, where the temperature of the first refrigerant is lower than that of the second refrigerant.

In one embodiment, the determining module 320 is further configured to:

In one embodiment, the control module 330 is further configured to:

In one embodiment, the determining module 320 is further configured to:

when the current operation mode is a heating mode and the outdoor environment temperature is less than or equal to a second preset temperature in the air conditioner operation parameters, determining a first heating mode as the target operation mode, wherein the multifunctional vapor-liquid separator 13 performs heat exchange treatment with the first refrigerant by using all the second refrigerants in the first heating mode; or alternatively, the first and second heat exchangers may be,

In one embodiment, the determining module 320 is further configured to:

when the first defrosting frequency is greater than or equal to the preset frequency, switching the target operation mode from the first heating mode to a second heating mode, and judging whether the second defrosting frequency in a fourth preset period is smaller than the preset frequency according to the fourth preset period at regular time, wherein the multifunctional vapor-liquid separator 13 performs heat exchange treatment by using part of the second refrigerant and the first refrigerant in the second heating mode;

and when the second defrosting frequency is greater than or equal to the preset frequency, switching the target operation mode from the second heating mode to a third heating mode, wherein the multifunctional vapor-liquid separator 13 does not perform heat exchange treatment on the second refrigerant and the first refrigerant in the third heating mode.

In one embodiment, the control module 330 is further configured to:

As shown in fig. 17, the embodiment of the present application provides a computer device, including a processor 711, a communication interface 712, a memory 713, and a communication bus 714, where the processor 711, the communication interface 712, and the memory 713 perform communication with each other through the communication bus 714;

A memory 713 for storing a computer program;

in one embodiment of the present application, the processor 711 is configured to implement the air conditioner control method provided in any one of the foregoing method embodiments when executing the program stored in the memory 713.

It will be appreciated by those skilled in the art that the structure shown in fig. 17 is merely a block diagram of a portion of the structure associated with the present application and is not limiting of the air conditioning system to which the present application is applied, and that a particular air conditioning system may include more or fewer components than shown, or may combine certain components, or have a different arrangement of components.

In one embodiment, the air conditioning control device provided herein may be implemented in the form of a computer program that is operable on an air conditioning system as shown in fig. 17. The memory of the air conditioning system may store various program modules constituting the air conditioning control apparatus, such as the acquisition module 310, the determination module 320, and the control module 330 shown in fig. 16. The computer program constituted by the respective program modules causes the processor to execute the steps in the air conditioner control method of the respective embodiments of the present application described in the present specification.

The air conditioning system shown in fig. 17 may perform acquisition of the outdoor environment temperature and the air conditioning operation parameters through the acquisition module 310 in the air conditioning control device shown in fig. 16. The air conditioning system may perform the determination of the target operating mode based on the outdoor ambient temperature and the air conditioning operating parameter via the determination module 320. The air conditioning system may control the multifunctional vapor-liquid separator 13 to perform heat exchange treatment on the first refrigerant provided by the evaporator and the second refrigerant provided by the condenser when the target operation mode is the preset heat exchange mode through the control module 330, wherein the temperature of the first refrigerant is lower than that of the second refrigerant.

The present application also provides a computer-readable storage medium having stored thereon a computer program which, when executed by a processor, implements the steps of the air conditioner control method provided by any one of the method embodiments described above.

The apparatus embodiments described above are merely illustrative, wherein the elements illustrated as separate elements may or may not be physically separate, and the elements shown as elements may or may not be physical elements, may be located in one place, or may be distributed over a plurality of network elements. Some or all of the modules may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

From the above description of embodiments, it will be apparent to those skilled in the art that the embodiments may be implemented by means of software plus a general purpose hardware platform, or may be implemented by hardware. Based on such understanding, the foregoing technical solution may be embodied essentially or in a part contributing to the related art in the form of a software product, which may be stored in a computer readable storage medium, such as ROM/RAM, a magnetic disk, an optical disk, etc., including several instructions for causing an air conditioning system (which may be a personal computer, a server, or a network device, etc.) to perform the method described in the respective embodiments or some parts of the embodiments.

It is to be understood that the terminology used herein is for the purpose of describing particular example embodiments only, and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises," "comprising," "includes," "including," and "having" are inclusive and therefore specify the presence of stated features, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and/or groups thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order described or illustrated, unless an order of performance is explicitly stated. It should also be appreciated that additional or alternative steps may be used.

The foregoing is only a specific embodiment of the utility model to enable those skilled in the art to understand or practice the utility model. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the utility model. Thus, the present utility model is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. An air conditioning system, the air conditioning system comprising:

2. The air conditioning system according to claim 1, wherein the multifunctional vapor-liquid separator comprises a vapor-liquid separator body and a capillary tube, the inlet of the vapor-liquid separator body is communicated with the four-way valve, the outlet of the vapor-liquid separator body is communicated with the compressor, the capillary tube is arranged at the inner bottom of the vapor-liquid separator body, liquid separating heads are respectively arranged at two ends of the capillary tube, the first end of the capillary tube is communicated with the indoor unit electronic expansion valve, the second end of the capillary tube is communicated with a first electromagnetic valve arranged outside the vapor-liquid separator body, and the first electromagnetic valve is also communicated with the outdoor unit electronic expansion valve.

3. The air conditioning system according to claim 2, further comprising a second solenoid valve, wherein a first end of the second solenoid valve is in communication with the first solenoid valve and the outdoor unit electronic expansion valve, respectively, and a second end of the solenoid valve is in communication with the first end of the capillary tube and the indoor unit electronic expansion valve, respectively.

4. An air conditioning system according to claim 3, wherein the outlet and inlet of the vapor-liquid separator body are provided with a temperature sensor for detecting the inlet and outlet temperatures of the vapor-liquid separator, respectively.

5. The air conditioning system according to claim 3, further comprising an enthalpy injection assembly in communication with the first solenoid valve, the second solenoid valve, the outdoor unit electronic expansion valve, and the compressor, respectively, for performing an enthalpy injection process on the compressor.

6. The air conditioning system according to claim 5, wherein the enthalpy-injection assembly includes a subcooler, a subcooling electronic expansion valve, and an enthalpy-injection electronic expansion valve, the subcooling electronic expansion valve being in communication with the first solenoid valve, the second solenoid valve, and the subcooler, respectively, the subcooler being in communication with the outdoor heat exchanger through an outdoor electronic expansion valve, and the subcooler being in communication with the compressor through the enthalpy-injection electronic expansion valve.

7. The air conditioning system of claim 6, further comprising a third solenoid valve having a first end in communication with the electronic vapor injection expansion valve and the subcooler, respectively, and a second end in communication with the vapor-liquid separator body.