Air conditioning system

Abstract

The application provides an air conditioning system, which comprises a circulation loop, the circulation loop comprising a compressor, a reversing valve, an indoor unit, a throttling device and an outdoor unit connected in sequence; a pressure expansion valve, one end of which is communicated with a pipeline between the throttling device and the outdoor unit, and the other end of which is communicated with a pipeline between the throttling device and the indoor unit; when the circulation loop is in a first working state, the pressure expansion valve is closed; when the circulation loop is in a second working state, and the pressure at one end of the pressure expansion valve connected with the outdoor unit is less than the pressure at one end of the pressure expansion valve connected with the indoor unit and less than a preset pressure value, the pressure expansion valve is turned on. The pressure expansion valve provided by the application can accelerate the migration of refrigerant when turned on, adjust the suction side pressure of the system, and avoid problems such as oil retention, solidification of lubricating oil, air leakage and the like, thereby improving the stability and safety of the system.

Description

TECHNICAL FIELD

[0001] The present application relates to the air conditioning technical field, and in particular to an air conditioning system. BACKGROUND

[0002] The current equipment processing technology level cannot guarantee perfect and flawless elimination of any leakage point. Although in most cases, slow outward leakage of refrigerant in the air conditioning pipeline will not cause safety accidents. However, the leakage of air in the environment into the air conditioning pipeline not only directly pollutes the circulating refrigerant, but also when the leakage amount is large enough, it will also bring safety hazards of combustion and explosion, especially for room air conditioners using flammable refrigerants. Therefore, it is necessary to avoid the occurrence of sub-atmospheric pressure (negative pressure) in the air conditioning system to avoid the leakage of air in the environment into the pipeline. However, as a new generation of split heat pump air conditioning system with great potential, there will be a phenomenon that the suction pressure is continuously low or even lower than the atmospheric pressure during the starting process, which exists safety hazards.

[0003] In addition, the suction pressure of the split heat pump air conditioning system is continuously low during the starting process, and once the saturation temperature corresponding to the suction pressure is lower than the pour point of the lubricating oil, the problems of oil retention, lubricating oil solidification and the like will occur, which not only hinders the normal work of the heat pump, but also can cause damage to the compressor and safety problems. SUMMARY

[0004] In view of the problems in the prior art, the purpose of the present application is to provide an air conditioning system, which solves the problems of oil retention and air leakage caused by continuously low suction pressure, and improves the working stability and safety of the system.

[0005] An air conditioning system is provided in the embodiments of the present application, which comprises:

[0006] A circulating loop, which comprises a compressor, a reversing valve, an indoor unit, a throttling device and an outdoor unit connected in sequence;

[0007] A pressure expansion valve, one end of which is communicated with the pipeline between the throttling device and the outdoor unit, and the other end of which is communicated with the pipeline between the throttling device and the indoor unit;

[0008] When the circulating loop is in a first working state, the pressure expansion valve is closed;

[0009] When the circulating loop is in a second working state, and the pressure of one end of the pressure expansion valve communicated with the outdoor unit is less than the pressure of one end of the pressure expansion valve communicated with the indoor unit and less than a preset pressure value, the pressure expansion valve is turned on.

[0010] In some embodiments, the pressure expansion valve comprises:

[0011] A valve body comprising a first cavity and a second cavity; the first cavity is provided with a first valve port, the first valve port is connected with a pipeline between the first end of the throttling device and the outdoor unit; the second cavity is provided with a second valve port, the second valve port is connected with a pipeline between the second end of the throttling device and the indoor unit;

[0012] An elastic diaphragm is arranged in the first cavity and separates the first cavity into a first sub-cavity and a second sub-cavity which are not connected;

[0013] A valve core is arranged on the side of the elastic diaphragm located in the second sub-cavity and connected with the elastic diaphragm;

[0014] When the total external force on the side of the elastic diaphragm close to the first sub-cavity is greater than the other side, the elastic diaphragm deforms towards the direction close to the second cavity, drives the valve core to move, and makes the second sub-cavity and the second cavity connected to open the pressure expansion valve;

[0015] When the total external force on the side of the elastic diaphragm close to the first sub-cavity is less than or equal to the other side, the elastic diaphragm deforms away from the direction of the second cavity, drives the valve core to move, and the valve core separates the second sub-cavity and the second cavity to close the pressure expansion valve.

[0016] In some embodiments, a connecting channel is arranged between the first cavity and the second cavity, and the maximum cross-sectional area of the valve core is greater than the maximum cross-sectional area of the connecting channel.

[0017] In some embodiments, the maximum cross-sectional area structure of the valve core is located in the second cavity.

[0018] In some embodiments, the valve core comprises a valve rod and a valve block, one end of the valve rod is connected with the elastic diaphragm, the other end of the valve rod is connected with the valve block, and the maximum cross-sectional area of the valve block is greater than the maximum cross-sectional area of the connecting channel.

[0019] In some embodiments, a first spring is arranged on the side of the elastic diaphragm close to the first sub-cavity, and two ends of the first spring are respectively connected with one end of the first cavity away from the second cavity and the elastic diaphragm.

[0020] In some embodiments, a second spring is arranged on the side of the valve block away from the valve rod, and two ends of the second spring are respectively connected with one end of the second cavity away from the first cavity and the valve block.

[0021] In some embodiments, the first sub-cavity is connected with the atmosphere.

[0022] In some embodiments, the first sub-cavity is provided with at least one through hole.

[0023] In some embodiments, the valve block is a conical structure.

[0024] The air conditioning system provided by the application has the following advantages:

[0025] The air conditioning system provided by the application is provided with a pressure expansion valve, and the pressure expansion valve is arranged at both ends of the throttling device. When the suction pressure of the system is low, the pressure expansion valve is turned on to accelerate the migration of refrigerant, thereby solving the problem of low suction pressure of the system, avoiding problems such as oil retention, solidification of lubricating oil, air leakage and the like, and improving the safety and reliability of the system. In addition, the turning on and turning off of the pressure expansion valve is realized through force balance of the system itself, without the need to increase electric control equipment, thereby saving cost and simplifying the control equipment of the system. BRIEF DESCRIPTION OF DRAWINGS

[0026] Other features, objects and advantages of the application will become more apparent from the following detailed description of non-limiting embodiments with reference to the drawings.

[0027] Figure 1 is a schematic diagram of the air conditioning system provided by an embodiment of the application when the air conditioning system is in refrigeration;

[0028] Figure 2 is a schematic diagram of the air conditioning system provided by an embodiment of the application when the air conditioning system is in heating;

[0029] Figure 3 is a schematic diagram of the pressure expansion valve when the pressure expansion valve is turned on according to an embodiment of the application;

[0030] Figure 4 is a schematic diagram of the pressure expansion valve when the pressure expansion valve is turned off according to an embodiment of the application;

[0031] Figure 5 is a schematic diagram of the force acting on the elastic diaphragm of the pressure expansion valve when the pressure expansion valve is turned off according to an embodiment of the application;

[0032] Figure 6 is a schematic diagram of the force acting on the elastic diaphragm of the pressure expansion valve when the pressure expansion valve is turned off according to another embodiment of the application;

[0033] Figure 7 is a schematic diagram of the force acting on the elastic diaphragm of the pressure expansion valve when the pressure expansion valve is turned off according to still another embodiment of the application.

[0034] Reference signs:

[0035] 10 compressor c connecting passage

[0036] 20 indoor unit 511 first valve port

[0037] 30 throttling device 512 second valve port

[0038] 40 outdoor unit 52 elastic diaphragm

[0039] 50 pressure expansion valve 53 valve core

[0040] 51 valve body 531 valve rod

[0041] a first cavity 532 valve block

[0042] a1 first sub-cavity 54 first spring

[0043] a2 second sub-cavity 55 through hole

[0044] b second cavity 60 reversing valve DETAILED DESCRIPTION

[0045] Example embodiments now will be described more fully hereinafter with reference to the accompanying drawings. Example embodiments, may, however, be implemented in many different forms and should not be construed as limited to the implementations set forth herein; rather, these implementations are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the example embodiments to those skilled in the art. Like reference numerals refer to like elements throughout the figures, and descriptions of the same or similar elements can be omitted.

[0046] To solve the problems in the prior art, the embodiment of the present application provides an air conditioning system, as shown in Figure 1 and Figure 2 The air conditioning system comprises:

[0047] a circulation loop, the circulation loop comprising a compressor 10, an indoor unit 20, a throttling device 30 and an outdoor unit 40 connected in sequence;

[0048] a pressure expansion valve 50, one end of which is in communication with a pipeline between the throttling device 30 and the outdoor unit 40, and the other end of which is in communication with a pipeline between the throttling device 30 and the indoor unit 20;

[0049] When the circulation loop is in a first working state, the pressure expansion valve 50 is closed;

[0050] When the circulation loop is in a second working state, and the pressure at one end of the pressure expansion valve 50 connected to the outdoor unit 40 is less than the pressure at one end of the pressure expansion valve 50 connected to the indoor unit 20 and less than a preset pressure value, the pressure expansion valve 50 is turned on.

[0051] Here, the first working state is a refrigeration working state, as shown in Figure 1As shown, in the refrigeration working state: the high-pressure refrigerant is discharged from the outlet of the compressor 10, enters the outdoor unit 40 through the reversing valve 60 (specifically, the reversing valve 60 can be a four-way reversing valve), is condensed in the outdoor unit 40, and flows out of the outdoor unit 40 in a high-pressure state; the high-pressure refrigerant at the outlet of the outdoor unit 40 is throttled by the throttling device 30, is reduced in pressure and temperature, and then enters the indoor unit 20 in a low-pressure state, and returns to the compressor 10 from the outlet of the indoor unit 20 through the reversing valve 60. The throttling device 30 is connected to the outdoor unit 40 and the indoor unit 20 respectively at two ends, and the pressure expansion valve 50 is in a closed state in the refrigeration working state, without affecting the flow of the refrigerant.

[0052] Here, the second working state is a heating working state, as shown in FIG. 2. Figure 2 As shown, in the heating working state: the high-pressure refrigerant is discharged from the outlet of the compressor 10, enters the indoor unit 20 through the reversing valve 60, is condensed in the indoor unit 20, and flows out of the indoor unit 20 in a high-pressure state; the high-pressure refrigerant at the outlet of the indoor unit 20 is throttled by the throttling device 30, is reduced in pressure and temperature, and then enters the outdoor unit 40 in a low-pressure state, and returns to the compressor 10 from the outlet of the outdoor unit 40 through the reversing valve 60. The pressure expansion valve 50 is connected to the pipeline between the throttling device 30 and the outdoor unit 40 and the pipeline between the throttling device 30 and the indoor unit 20 at two ends, and the pressure difference at the two ends of the pressure expansion valve 50 is affected by the refrigerant pressures at the two ends of the indoor unit 20 and the outdoor unit 40; when the pressure at the one end of the pressure expansion valve 50 connected to the outdoor unit 40 is less than the pressure at the one end of the pressure expansion valve 50 connected to the indoor unit 20 and is less than a preset pressure value (the suction side pressure is low), the pressure expansion valve 50 is turned on, accelerating the migration of the refrigerant to the outdoor unit 40, solving the problem of the continuously low suction side pressure of the system, and avoiding problems such as oil stagnation, lubricating oil solidification, air leakage, and the like, thereby improving the safety and reliability of the system. In addition, the turning on and turning off of the pressure expansion valve 50 is realized through force balance of the system itself, without the need to increase electric control equipment, saving costs and simplifying the control equipment of the system.

[0053] Further, as shown in FIG. 3, Figures 3 to 7 In some embodiments, the pressure expansion valve 50 includes:

[0054] The valve body 51 includes a first cavity a and a second cavity b; the first cavity a is provided with a first valve port 511 connected to the pipeline between the first end of the throttling device 30 and the outdoor unit 40; the second cavity b is provided with a second valve port 512 connected to the pipeline between the second end of the throttling device 30 and the indoor unit 20, that is, the first valve port 511 is in communication with the first end of the outdoor unit 40, and the second valve port 512 is in communication with the first end of the indoor unit.

[0055] The elastic diaphragm 52 is arranged in the first cavity a and separates the first cavity a into the first sub-cavity a1 and the second sub-cavity a2 which are not connected;

[0056] The valve core 53 is arranged on the side of the elastic diaphragm 52 located in the second sub-cavity a2 and is fixedly connected with the elastic diaphragm 52;

[0057] When the total external force on the side of the elastic diaphragm 52 located in the first sub-cavity a1 is greater than that on the other side, the elastic diaphragm 52 deforms towards the direction close to the second cavity b, drives the valve core 53 to move and makes the second sub-cavity a2 and the second cavity b connected to open the pressure expansion valve 50.

[0058] Conversely, the valve core 53 separates the second sub-cavity a2 and the second cavity b to close the pressure expansion valve 50. That is, when the total external force on the side of the elastic diaphragm 52 located in the first sub-cavity a1 is less than or equal to that on the other side, the pressure expansion valve 50 is closed.

[0059] The pressure expansion valve 50 is arranged to communicate with the pipeline between the throttling device 30 and the outdoor unit 40 at one end and with the pipeline between the throttling device 30 and the indoor unit 20 at the other end, so that the refrigerant pressure at both ends of the pressure expansion valve 50 affects the force condition of the elastic diaphragm 52. When the system suction pressure is low, the total external force on the side of the elastic diaphragm 52 located in the first sub-cavity a1 is greater than that on the other side, so that the pressure expansion valve 50 is opened to accelerate the migration of the refrigerant, solve the problem of the continuous low suction side pressure of the system, avoid the problems of oil stagnation, lubricating oil solidification, air leakage and the like, and improve the safety and reliability of the system. Moreover, the opening and closing of the pressure expansion valve is realized by the force balance of the system itself, without the need to increase the electric control equipment, saving the cost and simplifying the control equipment of the system.

[0060] The specific structure of the pressure expansion valve 50 will be introduced below.

[0061] As shown in Figure 3 and Figure 4 , a connecting channel c is arranged between the first cavity a and the second cavity b, and the maximum cross-sectional area of the valve core 53 is greater than that of the connecting channel c. By moving the valve core 53, the structure of the valve core 53 with the maximum cross-sectional area can block the connecting channel c to separate the first cavity a and the second cavity b, so as to close the pressure expansion valve 50; or by moving the valve core 53, the structure of the valve core 53 with the maximum cross-sectional area moves away from the connecting channel c to make the first cavity a and the second cavity b connected. Specifically, the structure with the maximum cross-sectional area of the valve core 53 is located in the second cavity b. Here, the structure with the maximum cross-sectional area refers to the structure of the valve core 53 with the maximum cross-sectional area.

[0062] Further, please continue to refer to Figure 3 and Figure 4In the embodiment of the present application, the valve core 53 comprises a valve rod 531 and a valve block 532, one end of the valve rod 531 is connected with the elastic diaphragm 52, and the other end of the valve rod 531 is connected with the valve block 532. The cross-sectional area of the valve rod 531 is smaller than that of the connecting channel; the valve block 532 is a conical structure, the cross-sectional area of the valve block 532 away from the valve rod 531 is larger than that of the connecting channel c, and the cross-sectional area of the side of the valve block 532 close to the valve rod 531 is smaller than that of the connecting channel c.

[0063] It should be noted that the valve core 53 is not limited to the structure shown in the embodiment of the present application, and those skilled in the art can reasonably set the shape of the valve core 53 according to the shape of the connecting channel between the first cavity a and the second cavity b, so that when the valve core 53 moves towards the second cavity b, the first cavity a and the second cavity b are connected; and when the valve core 53 moves away from the second cavity b, the first cavity a and the second cavity b are disconnected.

[0064] Further, the elastic diaphragm 52 has good elastic deformation ability, deforms when subjected to external force, and restores to the original state when the external force disappears. The material of the elastic diaphragm 52 can be metal or non-metal. The elastic deformation ability of the elastic diaphragm 52 enables the valve core 53 to move to open or close the pressure expansion valve 50.

[0065] In some embodiments, the first sub-cavity a1 is connected with the atmosphere. As shown in Figure 3 and Figure 4 The first sub-cavity a1 is provided with at least one through hole 55, so that the first sub-cavity a1 is connected with the atmosphere.

[0066] Please refer to Figure 4 The elastic diaphragm 52 is provided with a first spring 54 on one side of the first sub-cavity a1, and the two ends of the first spring 54 are respectively connected with one end of the first sub-cavity a1 away from the second cavity b and the elastic diaphragm 52.

[0067] Based on the above introduction of the pressure expansion valve 50, the force on the elastic diaphragm 52 is introduced as follows. As shown in Figure 5As shown, when the elastic diaphragm 52 is in equilibrium (force balance), the first spring 54 is in a free state (no compression or extension). At this time, the elastic diaphragm 52 will be subjected to a downward atmospheric pressure force Ap1 and an upward cavity pressure force Ap2. Since the first valve port 511 is connected to the first end of the outdoor unit 40, the cavity pressure Ap2 is the pressure at the first end of the outdoor unit 40. When the atmospheric pressure force Ap1 on the elastic diaphragm 52 is greater than the cavity pressure force Ap2, the middle part of the elastic diaphragm 52 will deform inward toward the second cavity b, thereby driving the valve core 53 to move toward the second cavity b, so that the connecting channel c connects the first cavity a and the second cavity b, and the pressure expansion valve 50 is turned on.

[0068] like Figure 6 As shown, when the elastic diaphragm 52 is in equilibrium (force balance), the first spring 54 is compressed. At this time, the elastic diaphragm 52 is subjected to a downward atmospheric pressure force Ap1, a downward spring force F, and an upward cavity pressure force Ap2. When the sum of the atmospheric pressure force Ap1 and the spring force F is greater than the cavity pressure Ap2, the middle part of the elastic diaphragm 52 will deform inward toward the second cavity b, thereby driving the valve core 53 to move toward the second cavity b, so that the connecting channel c connects the first cavity a and the second cavity b.

[0069] like Figure 7 As shown, when the elastic diaphragm 52 is in equilibrium (force balance), the first spring 54 is in a stretched state. At this time, the elastic diaphragm 52 is subjected to a downward atmospheric pressure force Ap1, an upward spring force F, and an upward cavity pressure force Ap2. When the sum of the cavity pressure force Ap2 and the spring force F is less than the atmospheric pressure force Ap1, the middle part of the elastic diaphragm 52 will deform inward toward the second cavity b, thereby driving the valve core 53 to move toward the second cavity b, so that the connecting channel c connects the first cavity a and the second cavity b. Therefore, the specific working process of valve body 51 is as follows: When the resultant force of the downward force on elastic diaphragm 52 is greater than the upward force on elastic diaphragm 52, elastic diaphragm 52 deforms downward, causing valve stem 531 and valve block 532 to move towards the second cavity b. Valve block 532 moves away from connecting channel c, connecting the first cavity a and the second cavity b, and pressure expansion valve 50 is activated. Furthermore, the greater the downward distance of valve stem 531, the greater the flow area of ​​valve body 51. Figure 3 As shown. Conversely, the elastic diaphragm 52 resets, and the pressure expansion valve 50 closes, as... Figure 4 As shown.

[0070] In another embodiment, the other side of the valve block 532 is provided with a second spring, and the two ends of the second spring are connected to the end of the second cavity b away from the first cavity a and the valve block 532 respectively. In this embodiment, the force acting on the elastic diaphragm 52 is also related to the force applied to the elastic diaphragm 52 by the second spring.

[0071] In some other embodiments, no spring is provided at both ends of the elastic diaphragm 52. In these embodiments, the force acting on the elastic diaphragm 52 is only related to the cavity pressure of the first sub-cavity a1 and the second sub-cavity a2. According to the specific force acting on both ends of the elastic diaphragm 52, the skilled person in the art sets the conduction and closing of the pressure expansion valve 50.

[0072] Further, as shown in Figure 1 and Figure 2 , the specific reversing valve 60 is a four-way valve, the first end of the four-way valve is connected to the exhaust end of the compressor 10, the second end of the four-way valve is connected to the intake end of the compressor 10, the third end of the four-way valve is connected to the second end of the indoor unit 20, and the fourth end of the four-way valve is connected to the second end of the outdoor unit 40. The four-way valve is used to control the flow direction of the refrigerant to achieve refrigeration or heating of the air conditioning system.

[0073] Further, the throttling device 30 is located between the first end of the indoor unit 20 and the first end of the outdoor unit 40. The throttling device 30 can be a capillary tube in particular.

[0074] The working process of the air conditioning system in the refrigeration working state will be introduced below. Figure 1 , Figures 3 to 7

[0075] As Figure 1 , Figures 3 to 7 ​As shown, in the cooling operation: high-pressure refrigerant is discharged from the outlet of compressor 10. The high-pressure refrigerant enters outdoor unit 40 through reversing valve 60, condenses in outdoor unit 40, and flows out of outdoor unit 40 at high pressure. The high-pressure refrigerant at the outlet of outdoor unit 40 is throttled by throttling device 30, reducing pressure and temperature, and then enters indoor unit 20 at low pressure. It then returns to compressor 10 from the outlet of indoor unit 20 through reversing valve 60. In the cooling state, the first valve port 511 of pressure expansion valve 50 is connected to the first end of outdoor unit 40, and the second valve port 512 of pressure expansion valve 50 is connected to the first end of indoor unit 20. Therefore, the second sub-cavity a2 is connected to the outdoor unit 40, meaning that the high-pressure refrigerant at the outlet of the outdoor unit 40 is located below the elastic diaphragm 52. The upward force AP2 exerted by the high-pressure refrigerant on the elastic diaphragm 52 is usually high. At this time, the preload of the first spring 54 can be set (which can be set according to the pour point of the lubricating oil, atmospheric pressure, etc.) so that the resultant force of the downward force on the elastic diaphragm 52 is not greater than the upward force. That is, when the pressure at the end of the pressure expansion valve 50 connected to the outdoor unit 40 is not less than the preset pressure value, the pressure expansion valve 50 closes without affecting the original refrigerant circuit.

[0076] The following is combined with Figure 2 , Figures 3 to 7 The workflow of an air conditioning system in heating mode is described. For example... Figure 2 , Figures 3 to 7 As shown, the working process of the air conditioning system in heating mode is as follows:

[0077] The outlet of the compressor 10 discharges high-pressure refrigerant, which enters the indoor unit 20 through the reversing valve 60. The high-pressure refrigerant is condensed in the indoor unit 20 and flows out of the indoor unit 20 in a high-pressure state. The high-pressure refrigerant at the outlet of the indoor unit 20 is throttled by the throttling device 30, is reduced in pressure and temperature, and then enters the outdoor unit 40 in a low-pressure state, and flows out of the outdoor unit 40 outlet through the reversing valve 60 back to the compressor 10. In the heating state, the first valve port 511 of the pressure expansion valve 50 and the first end of the outdoor unit 40 are in communication, i.e. the low-pressure refrigerant at the first end of the outdoor unit 40 is below the elastic diaphragm 52. By setting the pre-tightening force of the first spring 54 (which can be set according to the pour point of the lubricating oil, atmospheric pressure, etc.), the upward force on the elastic diaphragm 52 is less than the downward force, i.e. when the pressure of the one end of the outdoor unit 40 connected to the pressure expansion valve 50 is less than the preset pressure value, the pressure expansion valve 50 is opened, and the lower the pressure, the greater the opening of the pressure expansion valve 50. When the upward force on the elastic diaphragm 52 increases, the opening of the pressure expansion valve 50 decreases until it is closed. Therefore, when the air conditioning system is started in the heating working state, once the evaporation pressure is too low (manifested as the upward force on the elastic diaphragm 52 is small and causes the elastic diaphragm 52 to deform), the pressure expansion valve 50 is opened, accelerating the migration of the refrigerant, and then as the start-up process continues, the evaporation pressure (suction pressure) rises, and the downward force on the elastic diaphragm 52 is not greater than the upward force, and then the pressure expansion valve 50 automatically returns to the closed state, which no longer affects the stable operation of the subsequent air conditioning system.

[0078] In summary, the air conditioning system provided by the present application has the following advantages:

[0079] The pressure expansion valve is arranged in communication with the pipeline between the throttling device and the outdoor unit at one end and in communication with the pipeline between the throttling device and the indoor unit at the other end. The refrigerant pressure at both ends of the pressure expansion valve affects the force on the elastic diaphragm. When the suction pressure of the system is low, the resultant force on the elastic diaphragm on one side of the first sub-cavity is greater than on the other side, so the pressure expansion valve is in communication, accelerating the migration of the refrigerant, solving the problem of low suction pressure of the system, avoiding problems such as oil retention, lubricating oil solidification, air leakage, etc., and improving the stability and reliability of the system. Moreover, the opening and closing of the pressure expansion valve is driven by the difference in force on the elastic diaphragm at both ends, without the need to increase the electrical control equipment, saving costs and simplifying the control equipment of the system.

[0080] The above is a further detailed description of the present application in conjunction with specific preferred embodiments, and the specific implementation of the present application should not be limited to these descriptions. For ordinary skilled persons in the technical field to which the present application belongs, a number of simple deductions or substitutions can be made without departing from the concept of the present application, and all of these should be considered within the protection scope of the present application.

Claims

1. An air conditioning system, characterized by, The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve.

2. The air conditioning system of claim 1, wherein, The application relates to a pressure expansion valve.

3. The air conditioning system of claim 2, wherein, The application relates to a pressure expansion valve.

4. The air conditioning system of claim 3, wherein, The application relates to a pressure expansion valve.

5. The air conditioning system of claim 4, wherein, The application relates to a pressure expansion valve.

6. The air conditioning system of claim 5, wherein, The application relates to a pressure expansion valve.

7. The air conditioning system according to any one of claims 1 to 6, characterized by The application relates to a pressure expansion valve.

8. The air conditioning system of claim 7, wherein, The application relates to a pressure expansion valve.

9. The air conditioning system of claim 4, wherein, The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. The application relates to a pressure expansion valve. 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