CN117387239A - Air conditioning system and related control method - Google Patents

Abstract

The application provides an air conditioning system and a related control method, wherein the air conditioning system comprises: an air conditioner main circuit comprising: the system comprises a compressor, a first four-way valve, an outdoor heat exchanger, an expansion valve and an indoor heat exchanger; a vortex tube branch comprising: a vortex tube and an indoor auxiliary heat exchanger; the input end of the vortex tube is arranged between the connecting paths of the first four-way valve and the indoor heat exchanger; the heat output end of the vortex tube is connected between the outdoor heat exchanger and the expansion valve through the indoor auxiliary heat exchanger; the auxiliary heat exchange loop exchanges heat with the refrigerant reflux path through the heat regenerator; the refrigerant reflux path is a flow path from the first four-way valve to the air inlet end of the compressor; the auxiliary heat exchange circuit includes: the first input end and the backheating output end are arranged between the outdoor heat exchanger and the expansion valve, and the second input end is connected with the cold output end of the vortex tube. The air conditioning system provided by the embodiment of the application can quickly heat indoor air when the air conditioner heats, and shortens cold air prevention time.

Description

Air conditioning system and related control method

Technical Field

The present disclosure relates to the field of air conditioning systems, and in particular, to an air conditioning system and a related control method.

Background

Most of air conditioning systems commonly used in the market at present are vapor compression systems, and mainly comprise a compressor, an outdoor heat exchanger, an electronic expansion valve, an indoor heat exchanger, a four-way valve and other components. When the existing air conditioning system is operated at low temperature for heating, the defects of insufficient air outlet temperature and long defrosting time can occur along with the reduction of the ambient temperature, and the electric auxiliary heat is usually started to supplement heat in order to improve the air outlet temperature, but the power consumption of the air conditioner is greatly increased by starting the electric auxiliary heat, and the energy efficiency is reduced; and the air conditioner generally has cold air prevention time of about 2 minutes during heating operation, and the air conditioner does not provide heat for the indoor during the cold air prevention time.

In view of this, a technology is needed to overcome the defect that the air outlet temperature is low during low-temperature heating operation, so that the indoor air is quickly heated during heating of the air conditioner, the cold air prevention time is shortened, and the thermal comfort level of a user is improved.

Disclosure of Invention

In order to overcome the problems in the related art, an object of the embodiments of the present application is to provide an air conditioning system, which can quickly heat indoor air when an air conditioner heats, and shorten the cold air prevention time.

An air conditioning system provided in a first aspect of an embodiment of the present application includes:

an air conditioner main circuit comprising: a compressor 10, a first four-way valve 20, an outdoor heat exchanger 30, an expansion valve 40, and an indoor heat exchanger 50;

a vortex tube branch comprising: a vortex tube 60 and an indoor auxiliary heat exchanger 70; the input end of the vortex tube is arranged between the connecting paths of the first four-way valve 20 and the indoor heat exchanger 30; the heat output end of the vortex tube is connected between the outdoor heat exchanger 30 and the expansion valve 40 through the indoor auxiliary heat exchanger 70;

an auxiliary heat exchange loop for performing heat exchange with the refrigerant return path through the heat regenerator 80; wherein, the refrigerant reflux path is a flow path from the first four-way valve 20 to the air inlet end of the compressor; the auxiliary heat exchange circuit includes: a first input and a regenerative output disposed between the outdoor heat exchanger 30 and the expansion valve 40, and a second input connected to the cold output of the vortex tube.

In one embodiment, a flow path control valve is further disposed in the auxiliary heat exchange circuit, and is configured to correspondingly switch a refrigerant flow path in the auxiliary heat exchange circuit in different operation modes of the air conditioning system.

In one embodiment, the flow path control valve includes a first control valve 31 and a second control valve 32;

the first control valve 31 is arranged between the first input end of the auxiliary heat exchange loop and the input end of the heat regenerator;

the second control valve 32 is arranged between the first input end and the backheating output end in the auxiliary heat exchange loop;

when the air conditioning system is operating in the heating mode, the second control valve 32 is opened and the first control valve 31 is closed.

In one embodiment, the input of the vortex tube is provided with a third control valve 33;

when the air conditioning system is operated in a cooling mode, the second control valve 32 and the third control valve 33 are closed, and the first control valve 31 is opened;

when the air conditioning system is operating in the heating mode, the second control valve 32 and the third control valve 33 are opened, and the first control valve 31 is closed.

In one embodiment, the flow path control valve is a second four-way valve 90;

the a end of the second four-way valve 90 is connected with a first input end in the auxiliary heat exchange loop, the b end of the second four-way valve 90 is connected with an input end of a regenerator in the auxiliary heat exchange loop, the c end of the second four-way valve 90 is connected with a regenerative output end in the auxiliary heat exchange loop, and the d end of the second four-way valve 90 is connected with an output end of the regenerator in the auxiliary heat exchange loop;

wherein, in the connection path between the c-end of the second four-way valve 90 and the regenerative output end in the auxiliary heat exchange loop, a first check valve 91 is disposed, and the flow direction of the first check valve is from the c-end of the second four-way valve 90 to the regenerative output end;

when the air conditioning system operates in the heating mode, the d end and the a end of the second four-way valve 90 are conducted, and the c end and the b end of the second four-way valve 90 are conducted.

In one embodiment, in the connection path between the regenerative output in the auxiliary heat exchange circuit and the first input in the auxiliary heat exchange circuit, a second one-way valve 92 is provided, flowing in the direction from the regenerative output to the first input;

when the air conditioning system operates in the cooling mode, the a end and the b end of the second four-way valve 90 are conducted, and the d end and the c end of the second four-way valve 90 are conducted.

In one embodiment, in the connection path between the b end of the second four-way valve 90 and the input end of the regenerator in the auxiliary heat exchange circuit, a third check valve 93 is disposed, which flows from the b end of the second four-way valve 90 to the input end of the regenerator in the auxiliary heat exchange circuit;

in the connection path between the cold output of the vortex tube and the second input in the auxiliary heat exchange circuit, a fourth one-way valve 94 is provided, flowing in the direction from the cold output to the second input.

In one embodiment, a bypass defrosting shunt is further arranged in the connecting path between the heat output end and the regenerative output end of the vortex tube branch, and the bypass defrosting shunt is connected with the outdoor heat exchanger 30 in parallel;

wherein a fifth control valve 35 is arranged on the bypass defrosting shunt, and a fourth control valve 34 is arranged between the heat output end and the outdoor heat exchanger 30;

when the air conditioning system is operated in the defrosting mode, the fourth control valve 34 is closed and the fifth control valve 35 is opened.

In one embodiment, the first four-way valve 20 is arranged in the connecting path between the compressors 10 and is provided with a liquid storage tank 100;

an outdoor fan is further arranged at the outdoor heat exchanger 30;

an indoor fan is further arranged at the indoor heat exchanger 50.

The air conditioner control method provided in the second aspect of the embodiment of the application includes: the air conditioning system according to any of the above embodiments includes:

acquiring an operation mode of an air conditioning system;

and setting a corresponding control valve according to the operation mode, so that a refrigerant flowing path in the current air conditioning system is matched with the operation mode.

The technical principle in the embodiment of the application is as follows:

referring to the main circuit of the air conditioner shown by the solid line ("-") in fig. 1, in the prior art, in the heating mode, the first four-way valve 20 is in the first connection state (i.e. the d-end and the c-end are turned on, the a-end and the b-end are turned on), the refrigerant (high temperature and high pressure gas) output by the compressor 10 flows into the indoor heat exchanger 50 through the dc-end of the first four-way valve 20 to perform condensation and heat release, and the indoor fan takes out the heat of the refrigerant in the indoor heat exchanger 50 to provide warm air for the indoor. The refrigerant flowing out of the indoor heat exchanger 50 flows into the expansion valve 40 to be throttled, the throttled refrigerant is cooled and depressurized, the throttled refrigerant enters the outdoor heat exchanger 30 to be evaporated, and the evaporated refrigerant flows back to the compressor 10 through the four-way valve.

In low-temperature heating operation, because the heating capacity in the initial stage is limited, the initial stage of starting heating cannot provide warm air meeting the user requirement, or cold air prevention time of about 2 minutes (namely, the air conditioner does not provide heat indoors in the period of time) is generally available, so that the heating requirement of the user cannot be met in time.

The beneficial effects of the embodiment of the application are that:

in the embodiment of the application, a vortex tube branch and an auxiliary heat exchange loop are added on the basis of the existing air conditioner main loop. When the air conditioning system operates in a heating mode, the refrigerant (high-temperature high-pressure gas state) discharged by the compressor 10 flows out through the first four-way valve 20 and is heated in two ways, one way enters the outdoor heat exchanger 30 through the air conditioning main loop, the other way is depressurized through the vortex tube 60 and subjected to cold-heat separation, the heat output end of the vortex tube separates out a first hot gas refrigerant with higher exhaust temperature than the compressor, and the first hot gas refrigerant enters the indoor auxiliary heat exchanger 70, so that the heating effect of the air conditioning system can be enhanced, the indoor air outlet temperature can be improved rapidly, and the cold air prevention time can be shortened. The cold output end of the vortex tube separates out a second hot gas refrigerant with lower exhaust temperature than the compressor, the second hot gas refrigerant flows into the heat regenerator 80 through the second input end of the auxiliary heat exchange loop, and exchanges heat with the refrigerant with relatively lower temperature in the refrigerant reflux path (the refrigerant to be refluxed to the compressor after being evaporated by the outdoor heat exchanger 30 in the air conditioner main loop) in the heat regenerator 80, thereby improving the air suction temperature and the air suction superheat degree of the refrigerant refluxed to the compressor 10, further improving the evaporation effect of the refrigerant before being refluxed to the compressor, and preventing the compressor from liquid impact risk.

Drawings

Fig. 1 is a schematic logic structure diagram of an air conditioning system according to an embodiment of the present application;

FIG. 2 is a schematic diagram of a vortex tube according to an embodiment of the present disclosure;

fig. 3 is a schematic diagram of another logic structure of an air conditioning system according to an embodiment of the present application;

fig. 4 is a schematic diagram of another logic structure of an air conditioning system according to an embodiment of the present application;

fig. 5 is a schematic diagram of another logic structure of an air conditioning system according to an embodiment of the present application;

fig. 6 is a schematic diagram of another logic structure of an air conditioning system according to an embodiment of the present application;

fig. 7 is a schematic diagram of another logic structure of an air conditioning system according to an embodiment of the present application;

fig. 8 is a flow chart of an air conditioner control method according to an embodiment of the present application.

Detailed Description

Preferred embodiments of the present application will be described in more detail below with reference to the accompanying drawings. While the preferred embodiments of the present application are shown in the drawings, it should be understood that the present application may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

The terminology used in the present application is for the purpose of describing particular embodiments only and is not intended to be limiting of the present application. As used in this application and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It should also be understood that the term "and/or" as used herein refers to and encompasses any or all possible combinations of one or more of the associated listed items.

It should be understood that although the terms "first," "second," "third," etc. may be used herein to describe various information, these information should not be limited by these terms. These terms are only used to distinguish one type of information from another. For example, a first message may also be referred to as a second message, and similarly, a second message may also be referred to as a first message, without departing from the scope of the present application. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present application, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.

It should be noted that, in all embodiments of the present application, "connected" may be understood as a direct connection or a pitch connection, and if a pitch connection is used, another element may exist between two "connected" elements.

It should be noted that, in all embodiments of the present application, "high temperature", "high pressure", "medium temperature", "medium pressure", "low temperature" and "low pressure" are relative concepts, and are not commonly defined in the industry, nor are specific corresponding pressure values/pressure ranges or temperature values/temperature ranges. For example, in the air conditioning system, if the former node describes the refrigerant as "high temperature" and the latter node describes the refrigerant as "medium temperature", it means that the refrigerant is cooled (e.g., condensed); if the latter node describes that the refrigerant is at a high temperature, the temperature of the refrigerant is unchanged. If the former node describes the refrigerant as being at the medium temperature and the latter node describes the refrigerant as being at the low temperature, the refrigerant is cooled (e.g. condensed); if the latter node describes that the refrigerant is at the medium temperature, the temperature of the refrigerant is unchanged. While the descriptions of "high temperature", "medium temperature" and "low temperature" may collectively describe the relative temperature relationships of at least three nodes within the air conditioning system over a 3 degree range. The same applies to "high pressure", "medium pressure" and "low pressure", and will not be described here again.

In practical application, the air conditioning main circuit of the air conditioning system includes: compressor, cross valve, outdoor heat exchanger, expansion valve and indoor heat exchanger.

In the cooling mode, the flow path of the refrigerant in the air conditioner main circuit is as follows: compressor, four-way valve, outdoor heat exchanger, expansion valve, indoor heat exchanger and compressor.

In the heating mode, the flow path of the refrigerant in the air conditioner main loop is as follows: compressor- & gtfour-way valve- & gtindoor heat exchanger- & gtexpansion valve- & gtoutdoor heat exchanger- & gtcompressor.

In the heating mode in the prior art, the first four-way valve 20 is in the first connection state (i.e. the d end is conducted with the c end, the a end is conducted with the b end), the refrigerant (high temperature and high pressure gas) output by the compressor 10 flows into the indoor heat exchanger 50 through the dc end of the first four-way valve 20 to perform condensation and heat release, and the indoor fan brings out the heat of the refrigerant in the indoor heat exchanger 50 to provide warm air for the indoor. The refrigerant flowing out of the indoor heat exchanger 50 flows into the expansion valve 40 to be throttled, the throttled refrigerant is cooled and depressurized, the throttled refrigerant enters the outdoor heat exchanger 30 to be evaporated, and the evaporated refrigerant flows back to the compressor 10 through the four-way valve.

In low-temperature heating operation, because the heating capacity in the initial stage is limited, the initial stage of starting heating cannot provide warm air meeting the user requirement, or cold air prevention time of about 2 minutes (namely, the air conditioner does not provide heat indoors in the period of time) is generally available, so that the heating requirement of the user cannot be met in time. In view of the foregoing, the embodiments of the present application provide an air conditioning system and a related control method capable of quickly heating indoor air during low-temperature heating, and refer to the following embodiments.

Example 1

Referring to fig. 1, an embodiment of an air conditioning system provided in an embodiment of the present application includes:

an air conditioner main circuit comprising: a compressor 10, a first four-way valve 20, an outdoor heat exchanger 30, an expansion valve 40, and an indoor heat exchanger 50;

a vortex tube branch comprising: a vortex tube 60 and an indoor auxiliary heat exchanger 70; the input end of the vortex tube is arranged between the connecting paths of the first four-way valve 20 and the indoor heat exchanger 30; the heat output end of the vortex tube is connected between the outdoor heat exchanger 30 and the expansion valve 40 through the indoor auxiliary heat exchanger 70;

an auxiliary heat exchange loop for performing heat exchange with the refrigerant return path through the heat regenerator 80; wherein, the refrigerant reflux path is a flow path from the first four-way valve 20 to the air inlet end of the compressor; the auxiliary heat exchange circuit includes: a first input and a regenerative output disposed between the outdoor heat exchanger 30 and the expansion valve 40, and a second input connected to the cold output of the vortex tube.

For ease of reading, the main air conditioning circuit is shown in fig. 1 by a solid line ("-"), the auxiliary heat exchange circuit is shown by a dashed line ("-") and the auxiliary heat exchange circuit is shown by a dot-and-dash line ("dot-and-dash line"). ^. — ^. - ") represents a vortex tube branch.

Regarding the first four-way valve 20, the first four-way valve 20 in the embodiment of the present application has four connection ports of a-terminal, b-terminal, c-terminal, and d-terminal. The four connection ports form a first connection state (i.e., the d end and the c end are conducted, the a end and the b end are conducted) and a second connection state (i.e., the d end and the a end are conducted, the c end and the b end are conducted), which correspond to the refrigerant flowing paths of the air conditioning system in a heat demand mode (e.g., a heating mode or a defrosting mode) and a non-heat demand mode (a refrigerating mode).

Regarding the vortex tube 60, in the embodiment of the present application, the refrigerant (high temperature and high pressure gas) discharged from the compressor flows out through the c end of the first four-way valve 20 and then is split into two paths, one path enters the indoor heat exchanger 50 through the air conditioner main circuit, and the other path flows into the vortex tube 60 through the input end of the vortex tube 60 for cold-heat separation. Illustratively, referring to FIG. 2, vortex tube 60 includes a cold output 71, a hot output 72, a vortex tube input 73, a vortex chamber 74, and a hot side regulator 75. Specifically, the high-pressure refrigerant tangentially enters from the vortex tube input end 73, expands in the vortex chamber 74 to perform high-speed circular motion to form a free vortex, the angular velocity of the central fluid close to the axis of the vortex tube is greater than the angular velocity of the peripheral fluid on the inner wall surface of the vortex tube, the central fluid and the peripheral fluid exchange energy, the peripheral fluid obtains energy, the temperature is increased, and the refrigerant flows out from the heat output end 72; the central refrigerant loses energy and the temperature is reduced, and the refrigerant reversely flows out of the cold output end 71 under the blocking action of the hot end regulating valve 75, so that rapid cold-hot separation can be realized. Further, the temperature and flow rate of the air flow at the outlet of the cold and hot ends of the vortex tube can be controlled by adjusting the opening degree of the hot end adjusting valve 75.

Regarding the regenerator 80, in the embodiment of the present application, heat exchange is performed in two refrigerant circuits through the regenerator, one is a refrigerant return path (a flow path of the refrigerant from the b end of the first four-way valve to the air inlet end of the compressor) in the main circuit of the air conditioner, and the other is an auxiliary heat exchange circuit (in the heating mode, the auxiliary heat exchange circuit flows through the refrigerant output from the cold output end of the vortex tube). The flow directions of the two refrigerant loops of the heat exchange are opposite, the temperature of the refrigerant output by the cold output end of the vortex tube is higher than the temperature of the refrigerant in the refrigerant backflow path, so that the suction temperature and suction superheat of the refrigerant flowing back to the compressor 10 are improved, the evaporation effect of the refrigerant (namely, the refrigerant in the refrigerant backflow path) before flowing back to the compressor is further improved, and the liquid impact risk of the compressor can be prevented. Illustratively, regenerator 80 may be a compact shell and tube heat exchanger or a plate heat exchanger.

In this embodiment, when the air conditioning system operates in the heating mode, the refrigerant (high temperature and high pressure gas) discharged from the compressor 10 flows out through the first four-way valve 20 and is heated in two ways, one way enters the indoor heat exchanger 50 through the air conditioning main circuit, and the other way enters the vortex tube branch through the vortex tube 60.

In the vortex tube branch, a first hot gas refrigerant with higher exhaust temperature than the compressor is separated from the heat output end of the vortex tube, and a second hot gas refrigerant with lower exhaust temperature than the compressor is separated from the cold output end of the vortex tube.

The first hot gas refrigerant enters the indoor auxiliary heat exchanger 70, and the heating air in the indoor auxiliary heat exchanger 70 is conveyed into the room through the indoor fan, so that the heating effect of the air conditioning system is enhanced, the indoor air outlet temperature is improved rapidly, and the cold air prevention time is shortened.

The second hot gas refrigerant flows into the regenerator 80 through the second input end of the auxiliary heat exchange loop, exchanges heat with a refrigerant with relatively low temperature in a refrigerant backflow path (a refrigerant to be refluxed to a compressor after being evaporated by the outdoor heat exchanger 30 in the air conditioner main loop) in the regenerator 80, improves the suction temperature and suction superheat degree of the refrigerant reflowing to the compressor 10, and further evaporates the refrigerant which is output by the outdoor heat exchanger and cannot be completely evaporated into gas, so that liquid can be prevented from entering the compressor, and the liquid impact risk of the compressor is reduced.

Example 2

Because the air conditioning system generally has two functions of a heating mode and a cooling mode at the same time, in practical application, the flow path of the refrigerant in the auxiliary heat exchange loop in different modes needs to be controlled by the flow path control valve, and the embodiment of the application provides a corresponding solution, please refer to fig. 1, 3 and 4, and based on embodiment 1, the air conditioning system in the embodiment of the application further includes: a flow path control valve. The flow path control valve arranged in the auxiliary heat exchange loop is used for correspondingly switching the refrigerant flowing path in the auxiliary heat exchange loop under different operation modes of the air conditioning system.

Specifically, the flow path control valve includes a first control valve 31 and a second control valve 32; the first control valve 31 is arranged between the first input end of the auxiliary heat exchange loop and the input end of the heat regenerator; the second control valve 32 is disposed between the first input and the regenerative output in the auxiliary heat exchange circuit.

Heating mode-as shown in fig. 1, when the air conditioning system is operating in the heating mode, the second control valve 32 is opened and the first control valve 31 is closed. The refrigerant (high temperature and high pressure gas) discharged from the compressor 10 flows out from the d end and the c end of the first four-way valve 20 and then is divided into two paths, one path supplies heat for the room through the indoor heat exchanger 50, and the condensed refrigerant throttles through the expansion valve 40 (the path is a main loop refrigerant); the other path enters a vortex tube branch through a vortex tube 60, and a first hot gas refrigerant with higher exhaust temperature than the compressor is separated from the heat output end of the vortex tube in the vortex tube branch and is collected with a main loop refrigerant output after passing through an indoor auxiliary heat exchanger 70 and an expansion valve. The cold output end of the vortex tube separates out a second hot gas refrigerant with lower temperature than the exhaust temperature of the compressor, and the second hot gas refrigerant is converged with the first hot gas refrigerant and the main loop refrigerant after passing through the heat regenerator 80. After the three refrigerants of the main circuit refrigerant, the first hot gas refrigerant and the second hot gas refrigerant are collected, the three refrigerants flow into the outdoor heat exchanger 30 through the second control valve 32, and then flow back to the compressor 10 through the a end and the b end of the first four-way valve 20.

Refrigeration mode-as shown in figure 3, further, the input of the vortex tube is provided with a third control valve 33, said second control valve 32 and third control valve 33 being closed and said first control valve 31 being open when the air conditioning system is operating in refrigeration mode. Refrigerant (high temperature and high pressure gas) discharged from the compressor 10 flows out through the d-end and the a-end of the first four-way valve 20, flows into the outdoor heat exchanger 30, and is condensed. The condensed refrigerant flows into the heat regenerator 80 through the first control valve 31, and exchanges heat with the refrigerant with relatively low temperature in the refrigerant return path (the refrigerant in the air conditioner main loop which is going to flow back to the compressor after passing through the indoor heat exchanger 50) in the heat regenerator 80; the refrigerant after heat exchange by the regenerator 80 flows into the expansion valve 40 to be throttled through the regenerative output end in the auxiliary heat exchange loop, and the throttled refrigerant flows back to the compressor 10 through the indoor heat exchanger 50 and the c end and the b end of the first four-way valve.

In the cooling mode, since the refrigerant entering the outdoor heat exchanger 30 is about eighty degrees celsius, the refrigerant exiting the outdoor heat exchanger 30 is about forty degrees celsius (i.e., the temperature of the refrigerant flowing into the regenerator 80 through the first control valve 31), and the refrigerant exiting the indoor heat exchanger 50 is about ten degrees celsius, after heat exchange is performed by the regenerator 80, the refrigerant flows into the indoor heat exchanger 50 through the regenerative output end of the auxiliary heat exchange circuit and the expansion valve 40, thereby helping to reduce the enthalpy and dryness of the refrigerant flowing into the indoor heat exchanger 50, and improving the heat exchange performance of the indoor heat exchanger 50 and the refrigerating capacity of the system.

Defrosting mode-as shown in fig. 4, a bypass defrosting shunt is further arranged in the connecting path between the heat output end and the regenerative output end of the vortex tube branch, and the bypass defrosting shunt is connected with the outdoor heat exchanger 30 in parallel; wherein a fifth control valve 35 is arranged on the bypass defrosting shunt, and a fourth control valve 34 is arranged between the heat output end and the outdoor heat exchanger 30; when the air conditioning system is operated in the defrosting mode, the first control valve 31 and the fourth control valve 34 are closed, and the second control valve 32, the third control valve 33 and the fifth control valve 35 are opened.

When the air conditioning system operates in a defrosting mode, the refrigerant (high-temperature high-pressure gas state) discharged by the compressor 10 flows out from the d end and the c end of the first four-way valve 20 and is divided into two paths, one path of the refrigerant passes through the indoor heat exchanger 50, and the condensed refrigerant is throttled by the expansion valve 40 (the path is a main loop refrigerant); the other path enters a vortex tube branch through a vortex tube 60, and a first hot gas refrigerant with higher exhaust temperature than the compressor is separated from the heat output end of the vortex tube in the vortex tube branch and is converged with a main loop refrigerant output after passing through the fifth control valve 35. The cold output end of the vortex tube separates out a second hot gas refrigerant with lower temperature than the exhaust temperature of the compressor, and the second hot gas refrigerant is converged with the first hot gas refrigerant and the main loop refrigerant after passing through the heat regenerator 80. After the three refrigerants of the main circuit refrigerant, the first hot gas refrigerant and the second hot gas refrigerant are collected, the three refrigerants flow into the outdoor heat exchanger 30 through the second control valve 32, and then flow back to the compressor 10 through the a end and the b end of the first four-way valve 20.

In the defrosting mode, a first hot gas refrigerant is separated from the heat output end of the vortex tube and enters the outdoor heat exchanger 30 to defrost through the fifth control valve 35; the second hot gas refrigerant separated from the cold output end of the vortex tube enters the heat regenerator 80 to exchange heat with the refrigerant at the outlet of the outdoor heat exchanger 30, and the refrigerant after heat exchange enters the outdoor heat exchanger 30 through the second control valve 32 to be further defrosted or evaporated. The refrigerant at the outlet of the outdoor heat exchanger 30 exchanges heat in the regenerator 80 and then flows back to the suction port of the compressor 10, and thus circulates. The vortex tube 60 is utilized to separate out the refrigerant with the temperature higher than the exhaust temperature of the compressor and enter the outdoor heat exchanger 30 for defrosting, thereby being beneficial to accelerating the defrosting speed and shortening the defrosting time; meanwhile, the refrigerant (in a gaseous state) with the cold output end of the vortex tube lower than the exhaust temperature of the compressor is utilized to exchange heat with the low-temperature refrigerant at the outlet of the outdoor heat exchanger 30 in the heat regenerator 80, so that the air suction temperature entering the compressor can be increased, and the liquid impact risk of the compressor is prevented. In addition, the vortex tube has the function of reducing pressure, and compared with the scheme that part of high-pressure compressor exhaust gas is directly used for entering an outdoor heat exchanger for defrosting in the prior art, the air conditioning system in the embodiment of the application has the advantages of reducing the pressure, reducing the air suction saturation temperature and increasing the superheat degree of the bottom of the compressor.

Example 3

In addition to the manner of controlling the flow paths of the refrigerant in the auxiliary heat exchange circuit in different modes by two control valves in embodiment 2, the embodiment of the present application provides a solution in which the four-way valve is used as the flow path control valve, referring to fig. 5, 6, 7 and 8, and based on embodiment 1, the air conditioning system in the embodiment of the present application further includes:

referring to fig. 5, the flow path control valve is a second four-way valve 90; the a end of the second four-way valve 90 is connected with a first input end in the auxiliary heat exchange loop, the b end of the second four-way valve 90 is connected with an input end of a regenerator in the auxiliary heat exchange loop, the c end of the second four-way valve 90 is connected with a regenerative output end in the auxiliary heat exchange loop, and the d end of the second four-way valve 90 is connected with an output end of the regenerator in the auxiliary heat exchange loop.

Wherein, in the connection path between the c-end of the second four-way valve 90 and the regenerative output end in the auxiliary heat exchange loop, a first check valve 91 is disposed, and the flow direction of the first check valve is from the c-end of the second four-way valve 90 to the regenerative output end; that is, in the heating mode or the defrosting mode, the path from the "regenerative output end" to the "c-end of the second four-way valve 90" is not conducted.

Wherein, in the connection path between the regenerative output end in the auxiliary heat exchange loop and the first input end in the auxiliary heat exchange loop, a second one-way valve 92 is arranged, which flows from the regenerative output end to the first input end; that is, in the cooling mode, the path from the "first input" to the "regenerative output" is not conductive.

Wherein, in the connection path between the b end of the second four-way valve 90 and the input end of the regenerator in the auxiliary heat exchange loop, a third one-way valve 93 is arranged, which flows from the b end of the second four-way valve 90 to the input end of the regenerator in the auxiliary heat exchange loop; in order to prevent the refrigerant that the cold output end of the vortex tube outputs from flowing backward when in heating mode or defrosting mode.

In the connection path between the cold output end of the vortex tube and the second input end of the auxiliary heat exchange loop, a fourth one-way valve 94 is arranged to flow from the cold output end to the second input end, so as to prevent the main loop refrigerant from flowing backwards to the vortex tube in the refrigeration mode.

As shown in fig. 5, further, in order to prevent the refrigerant flowing back to the compressor from not completely evaporating, the first four-way valve 20 is provided with a liquid storage tank 100 flowing back to the connection path between the compressors 10; the device is used for separating gas and liquid of the refrigerant and reducing the liquid impact risk of the compressor. Further, an outdoor fan 110 is further disposed at the outdoor heat exchanger 30, and an indoor fan 120 is further disposed at the indoor heat exchanger 50.

Heating mode—as shown in fig. 6, the first four-way valve 20 is in the first connection state (i.e., the d and c ends are turned on, and the a and b ends are turned on), and the second four-way valve 90 is in the first connection state (i.e., the d and a ends are turned on, and the c and b ends are turned on). The third control valve 33 and the fourth control valve 34 are opened, and the fifth control valve 35 is closed.

The refrigerant (high temperature and high pressure gas) discharged from the compressor 10 flows out from the d end and the c end of the first four-way valve 20 and then is divided into two paths, one path supplies heat for the room through the indoor heat exchanger 50, and the condensed refrigerant throttles through the expansion valve 40 (the path is a main loop refrigerant); the other path enters a vortex tube branch through a vortex tube 60, and a first hot gas refrigerant with higher exhaust temperature than the compressor is separated from the heat output end of the vortex tube in the vortex tube branch and is collected with a main loop refrigerant output after passing through an indoor auxiliary heat exchanger 70 and an expansion valve. Since the first check valve 91 is provided, no refrigerant flows into the b end of the second four-way valve 90 at the c end of the second four-way valve 90. The main circuit refrigerant and the first hot gas refrigerant are collected and flow to the outdoor heat exchanger 30. The cold output end of the vortex tube separates out a second hot gas refrigerant with lower temperature than the exhaust temperature of the compressor, and the second hot gas refrigerant is converged with the first hot gas refrigerant and the main loop refrigerant through the d end and the a end of the second four-way valve 90 after passing through the heat regenerator 80. After the three refrigerants of the main loop refrigerant, the first hot gas refrigerant and the second hot gas refrigerant are collected, the three refrigerants pass through the outdoor heat exchanger 30, pass through the end a and the end b of the first four-way valve 20, pass through the heat regenerator 80 and the liquid storage tank 100, and flow back to the compressor 10.

Cooling mode—as shown in fig. 7, the first four-way valve 20 is in the second connection state (i.e., the d and a ends are conductive, and the c and b ends are conductive), and the second four-way valve 90 is in the second connection state (i.e., the a and b ends are conductive, and the d and c ends are conductive). The third control valve 33, the fourth control valve 34 and the fifth control valve 35 are closed.

Refrigerant (high temperature and high pressure gas) discharged from the compressor 10 flows out through the d-end and the a-end of the first four-way valve 20, flows into the outdoor heat exchanger 30, and is condensed. The condensed refrigerant flows into the heat regenerator 80 through the end a and the end b of the second four-way valve, and exchanges heat with the refrigerant with relatively low temperature in the refrigerant reflux path (the refrigerant to be refluxed to the compressor after passing through the indoor heat exchanger 50 in the air conditioner main loop) in the heat regenerator 80; the refrigerant after heat exchange by the regenerator 80 flows into the expansion valve 40 to be throttled through the d end and the c end of the second four-way valve and the regenerative output end in the auxiliary heat exchange loop, and the throttled refrigerant flows back to the compressor 10 through the indoor heat exchanger 50, the c end and the b end of the first four-way valve and the liquid storage tank 100.

Defrosting mode—as shown in fig. 6 (defrosting mode is similar to heating mode in refrigerant flow path, only some of the control valves are opened or closed differently), the first four-way valve 20 is in the first connection state (i.e., d-terminal and c-terminal are conductive, a-terminal and b-terminal are conductive), and the second four-way valve 90 is in the first connection state (i.e., d-terminal and a-terminal are conductive, c-terminal and b-terminal are conductive). The third control valve 33 and the fifth control valve 35 are opened, and the fourth control valve 34 is closed.

Refrigerant (high temperature and high pressure gas) discharged from the compressor 10 flows out from the d end and the c end of the first four-way valve 20 and then is divided into two paths, one path of refrigerant passes through the indoor heat exchanger 50, and the condensed refrigerant is throttled by the expansion valve 40 (the path is a main loop refrigerant); the other path enters a vortex tube branch through a vortex tube 60, and a first hot gas refrigerant with higher exhaust temperature than the compressor is separated from the heat output end of the vortex tube in the vortex tube branch and is converged with a main loop refrigerant output after passing through the fifth control valve 35. The cold output end of the vortex tube separates out a second hot gas refrigerant with lower temperature than the exhaust temperature of the compressor, and the second hot gas refrigerant is converged with the first hot gas refrigerant and the main loop refrigerant through the d end and the a end of the second four-way valve 90 after passing through the heat regenerator 80. After the three refrigerants of the main circuit refrigerant, the first hot gas refrigerant and the second hot gas refrigerant are collected, the three refrigerants flow into the outdoor heat exchanger 30, and then flow back to the compressor 10 through the end a and the end b of the first four-way valve 20.

In this embodiment of the present application, another manner of controlling the flow path of the refrigerant in the auxiliary heat exchange loop in different modes is provided, and the technical effects that can be achieved by the heating mode, the cooling mode and the defrosting mode are consistent with those of embodiment 2, which is not described herein again.

Example 4

On the basis of the air conditioning systems corresponding to fig. 1 to 4, the embodiment of the present application further sets a corresponding air conditioning control method based on the air conditioning system, referring to fig. 8, and one embodiment of the air conditioning control method based on the air conditioning system in the embodiment of the present application includes:

801. acquiring an operation mode of an air conditioning system;

the operation module comprises a refrigeration mode, a heating mode and a defrosting mode.

If the operation mode is a cooling mode, executing step 802;

if the operation mode is a heating mode, step 803 is executed.

If the operation mode is the defrosting mode, step 804 is performed.

802. If the operation mode is the refrigeration mode, a flow path control valve in the auxiliary heat exchange loop is arranged to be in a non-heat demand mode, and the third control valve, the fourth control valve and the fifth control valve are closed.

Specifically, the non-heat demand mode is a cooling mode. It is possible to control the second control valve and the third control valve to be closed and the first control valve to be opened with reference to embodiment 2. It is also possible to refer to embodiment 3 to set the second four-way valve 90 in the second connection state (i.e., the a-terminal and the b-terminal are conducted, and the d-terminal and the c-terminal are conducted). The flow path control valve may be provided in a variety of ways, and is not limited herein.

803. If the operation mode is a heating mode, a flow path control valve in the auxiliary heat exchange loop is set to be in a heat demand mode, a third control valve and a fourth control valve are opened, and a fifth control valve is closed.

Specifically, the non-heat demand mode is a heating mode or a defrosting mode. It is possible to control the second control valve to be opened and the first control valve to be closed with reference to embodiment 2. It is also possible to refer to embodiment 3 to set the second four-way valve 90 in the first connection state (i.e., the d-terminal and the a-terminal are conducted, and the c-terminal and the b-terminal are conducted). The flow path control valve may be provided in a variety of ways, and is not limited herein.

804. If the operation mode is the defrosting mode, a flow path control valve in the auxiliary heat exchange loop is set to be in a heat demand mode, a third control valve and a fifth control valve are opened, and a fourth control valve is closed.

Specifically, the non-heat demand mode is a heating mode or a defrosting mode. It is possible to control the second control valve and the third control valve to be opened and the first control valve to be closed with reference to embodiment 2. It is also possible to refer to embodiment 3 to set the second four-way valve 90 in the first connection state (i.e., the d-terminal and the a-terminal are conducted, and the c-terminal and the b-terminal are conducted). The flow path control valve may be provided in a variety of ways, and is not limited herein.

The specific flow paths and state changes of the refrigerant in the embodiments of the present application may refer to the above embodiments 1 to 4, and will not be described herein again.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present application unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures. In the description of the present application, it should be understood that, where azimuth terms such as "front, rear, upper, lower, left, right", "transverse, vertical, horizontal", and "top, bottom", etc., indicate azimuth or positional relationships generally based on those shown in the drawings, only for convenience of description and simplification of the description, these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present application; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.

Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

In addition, the terms "first", "second", etc. are used to define the components, and are merely for convenience of distinguishing the corresponding components, and unless otherwise stated, the terms have no special meaning, and thus should not be construed as limiting the scope of the present application. The foregoing description is only of the preferred embodiments of the present application and is not intended to limit the same, but rather, various modifications and variations may be made by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application should be included in the protection scope of the present application.

Claims (10)

1. An air conditioning system, comprising:

an air conditioner main circuit comprising: a compressor (10), a first four-way valve (20), an outdoor heat exchanger (30), an expansion valve (40), and an indoor heat exchanger (50);

a vortex tube branch comprising: a vortex tube (60) and an indoor auxiliary heat exchanger (70); the input end of the vortex tube is arranged between the connecting paths of the first four-way valve (20) and the indoor heat exchanger (30); the heat output end of the vortex tube is connected between the outdoor heat exchanger (30) and the expansion valve (40) through the indoor auxiliary heat exchanger (70);

the auxiliary heat exchange loop exchanges heat with the refrigerant reflux path through a heat regenerator (80); the refrigerant reflux path is a flow path from the first four-way valve (20) to the air inlet end of the compressor; the auxiliary heat exchange circuit includes: a first input and a regenerative output disposed between the outdoor heat exchanger (30) and the expansion valve (40), and a second input connected to the cold output of the vortex tube.

2. An air conditioning system according to claim 1, wherein a flow path control valve is further provided in the auxiliary heat exchange circuit, for switching the refrigerant flow path in the auxiliary heat exchange circuit correspondingly in different operation modes of the air conditioning system.

3. An air conditioning system according to claim 2, wherein,

the flow path control valve includes a first control valve (31) and a second control valve (32);

the first control valve (31) is arranged between the first input end in the auxiliary heat exchange loop and the input end of the heat regenerator;

the second control valve (32) is arranged between the first input end and the backheating output end in the auxiliary heat exchange loop;

when the air conditioning system is operated in a heating mode, the second control valve (32) is opened, and the first control valve (31) is closed.

4. An air conditioning system according to claim 3, characterized in that the input of the vortex tube is provided with a third control valve (33);

when the air conditioning system is in a refrigeration mode, the second control valve (32) and the third control valve (33) are closed, and the first control valve (31) is opened;

when the air conditioning system is operated in a heating mode, the second control valve (32) and the third control valve (33) are opened, and the first control valve (31) is closed.

5. An air conditioning system according to claim 2, wherein,

the flow path control valve is a second four-way valve (90);

the end a of the second four-way valve (90) is connected with a first input end in the auxiliary heat exchange loop, the end b of the second four-way valve (90) is connected with an input end of a regenerator in the auxiliary heat exchange loop, the end c of the second four-way valve (90) is connected with a regenerative output end in the auxiliary heat exchange loop, and the end d of the second four-way valve (90) is connected with an output end of the regenerator in the auxiliary heat exchange loop;

wherein, in the connection path between the c end of the second four-way valve (90) and the regenerative output end in the auxiliary heat exchange loop, a first one-way valve (91) which flows from the c end of the second four-way valve (90) to the regenerative output end is arranged;

when the air conditioning system operates in a heating mode, the d end and the a end of the second four-way valve (90) are conducted, and the c end and the b end of the second four-way valve (90) are conducted.

6. An air conditioning system according to claim 5, wherein,

a second one-way valve (92) flowing from the regenerative output end to the first input end is arranged in a connecting path between the regenerative output end in the auxiliary heat exchange loop and the first input end in the auxiliary heat exchange loop;

when the air conditioning system operates in a refrigeration mode, the end a and the end b of the second four-way valve (90) are conducted, and the end d and the end c of the second four-way valve (90) are conducted.

7. An air conditioning system according to claim 5, wherein,

a third one-way valve (93) which flows from the b end of the second four-way valve (90) to the input end of the regenerator in the auxiliary heat exchange loop is arranged in the connecting path of the b end of the second four-way valve (90) and the input end of the regenerator in the auxiliary heat exchange loop;

in the connection path between the cold output of the vortex tube and the second input in the auxiliary heat exchange circuit, a fourth one-way valve (94) is provided flowing from the cold output to the second input.

8. An air conditioning system according to claim 5, wherein,

a bypass defrosting shunt is further arranged in a connecting path between the heat output end and the regenerative output end of the vortex tube branch, and the bypass defrosting shunt is connected with the outdoor heat exchanger (30) in parallel;

wherein a fifth control valve (35) is arranged on the bypass defrosting shunt, and a fourth control valve (34) is arranged between the heat output end and the outdoor heat exchanger (30);

when the air conditioning system is in a defrosting mode, the fourth control valve (34) is closed, and the fifth control valve (35) is opened.

9. An air conditioning system according to claim 1, characterized in that the first four-way valve (20) is returned to the connection path between the compressors (10), and a liquid storage tank (100) is provided;

an outdoor fan is further arranged at the outdoor heat exchanger (30);

an indoor fan is further arranged at the indoor heat exchanger (50).

10. An air conditioning control method, implemented based on the air conditioning system according to any one of claims 1 to 9, comprising:

acquiring an operation mode of an air conditioning system;

and setting a corresponding control valve according to the operation mode, so that a refrigerant flowing path in the current air conditioning system is matched with the operation mode.