An air conditioning system

Abstract

The present invention discloses an air conditioning system, which relates to the field of air conditioning technology and can improve user comfort to at least a certain extent. The air conditioning system includes: a compressor, a reversing assembly, an indoor heat exchanger, an outdoor heat exchanger assembly, a defrost branch, and a bypass branch. The reversing assembly has first to fourth valve ports, the first valve port is connected to the exhaust port, the fourth valve port is connected to the intake port, the first end of the indoor heat exchanger is connected to the second valve port, the outdoor heat exchanger assembly includes a first part and a second part, the first end of the first part is connected to the third valve port, the first end of the defrost branch is connected to the exhaust port, the second end of the defrost branch is connected to the pipeline between the first throttle valve and the second end of the first part, the first end of the bypass branch is connected to the first end of the second part, and the second end of the bypass branch is connected to the pipeline between the first throttle valve and the second end of the first part. The air conditioning system of the present invention is used for air conditioning.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning, and in particular to an air conditioning system. Background Art

[0002] When an air conditioning system is operating in heating mode, frost will form on the outdoor heat exchanger assembly when the ambient temperature and humidity reach certain conditions. In related technologies, air conditioning systems use reverse defrosting to defrost the outdoor heat exchanger assembly. This method reverses the flow of the refrigerant used in heating, supplies the refrigerant discharged from the compressor to the outdoor heat exchanger assembly, and uses the heat from the compressor to defrost the outdoor heat exchanger assembly. During reverse defrosting, the air conditioning system stops heating the room and requires the indoor heat exchanger to absorb some heat from the room, lowering the indoor temperature, severely affecting indoor thermal comfort, and reducing the user experience. Summary of the Invention

[0003] Embodiments of the present invention provide an air conditioning system that can improve user comfort to at least a certain extent.

[0004] To achieve the above objectives, the embodiments of the present invention adopt the following technical solutions:

[0005] An embodiment of the present application provides an air-conditioning system, comprising: a compressor, a reversing assembly, an indoor heat exchanger, an outdoor heat exchanger assembly, a defrost branch, and a bypass branch. The compressor has an intake port and an exhaust port, the reversing assembly has first to fourth valve ports, the first valve port is connected to the exhaust port, the fourth valve port is connected to the intake port, the first end of the indoor heat exchanger is connected to the second valve port, the outdoor heat exchanger assembly includes a first part and a second part, the first end of the first part is connected to the third valve port, a first on-off valve is connected in series between the first end of the second part and the third valve port, a first throttle valve is connected between the second end of the first part and the second end of the indoor heat exchanger, and a second throttle valve is connected between the second end of the second part and the second end of the indoor heat exchanger, the first end of the defrost branch is connected to the exhaust port, the second end of the defrost branch is connected to the pipeline between the first throttle valve and the second end of the first part, and the second on-off valve is connected in series on the defrost branch, the first end of the bypass branch is connected to the first end of the second part, the second end of the bypass branch is connected to the pipeline between the first throttle valve and the second end of the first part, and the third throttle valve is connected in series on the bypass branch.

[0006] The air conditioning system provided by the embodiments of the present application utilizes an outdoor heat exchanger assembly comprising a first portion and a second portion arranged in parallel. When defrosting the first portion, the air conditioning system utilizes a defrost branch to bypass a portion of the refrigerant from the compressor's exhaust port to the first portion for defrosting. At this point, the second portion can function as an evaporator to continue the air conditioning system's heating cycle. When defrosting the second portion, the air conditioning system utilizes the latent heat of the high-pressure, medium-temperature refrigerant flowing out of the indoor heat exchanger to defrost the second portion. At this point, the first portion can function as an evaporator to continue the air conditioning system's heating cycle. This allows the indoor heat exchanger to maintain heating the room while alternately defrosting the first and second portions. This prevents the air conditioning system from affecting the indoor temperature during the defrosting process, maintaining a high indoor temperature and improving user comfort. Furthermore, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor's exhaust port is used to defrost the first portion, resulting in a significant defrosting effect. The high-pressure, medium-temperature refrigerant flowing out of the indoor heat exchanger is used to defrost the second portion, resulting in a significant defrosting effect. Therefore, through the defrosting method that combines low-pressure sensible heat with high-pressure waste heat, not only can the advantages of waste heat defrosting and sensible heat defrosting be utilized, but also the serious waste of waste heat defrosting capacity, poor reliability of sensible heat defrosting, and narrow applicable working conditions can be avoided, thereby improving the defrosting speed and reliability of the air-conditioning system to a certain extent.

[0007] In some embodiments, the first portion is located directly above the second portion; or, the first portion is located directly below the second portion.

[0008] In some embodiments, the second end of the bypass branch is connected to a pipeline between the second end of the defrost branch and the second end of the first portion.

[0009] In some embodiments, the reversing component is a four-way reversing valve.

[0010] In some embodiments, the first throttle valve, the second throttle valve, and the third throttle valve are all electronic expansion valves.

[0011] In some embodiments, the first part and the second part are two independent heat exchangers, or the first part and the second part are two parts of the same heat exchanger.

[0012] In some embodiments, the first on-off valve is a two-way valve; and / or the second on-off valve is a solenoid valve.

[0013] In some embodiments, the first throttle valve and the second throttle valve are connected to the second end of the indoor heat exchanger through a same subcooler.

[0014] In some embodiments, a gas-liquid separator is further included, which is arranged between the compressor and the reversing assembly. The gas-liquid separator has a liquid inlet and a gas outlet. The liquid inlet is connected to the fourth valve port, and the gas outlet is connected to the air intake.

[0015] In some embodiments, an oil-gas separator is further included, which has an inlet, a gas exhaust port and an oil outlet, wherein the inlet is connected to the exhaust port, the gas exhaust port is connected to the first valve port, and the oil outlet is connected to the intake port. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 A schematic diagram of the composition of an air conditioning system provided in the first embodiment of the present application;

[0017] Figure 2 A schematic diagram of the composition of an air conditioning system provided in the second embodiment of the present application;

[0018] Figure 3 A schematic diagram of the cooling mode of the air-conditioning system provided in the first embodiment of the present application;

[0019] Figure 4 A schematic diagram of the cooling mode of the air-conditioning system provided in the second embodiment of the present application;

[0020] Figure 5 A schematic diagram of a heating mode of an air-conditioning system provided in the first embodiment of the present application;

[0021] Figure 6 A schematic diagram of a heating mode of an air-conditioning system provided in a second embodiment of the present application;

[0022] Figure 7 A schematic diagram of defrosting a first part of an air conditioning system provided in a first embodiment of the present application;

[0023] Figure 8 A schematic diagram of defrosting the first part of the air conditioning system provided in the second embodiment of the present application;

[0024] Figure 9 A schematic diagram of the air conditioning system provided in the first embodiment of the present application defrosting the second part;

[0025] Figure 10 A schematic diagram of the air conditioning system provided in the second embodiment of the present application defrosting the second part;

[0026] Figure 11 A flow chart of a first defrost control method for an air-conditioning system provided in an embodiment of the present application;

[0027] Figure 12A flow chart of a second defrost control method for an air-conditioning system provided in an embodiment of the present application;

[0028] Figure 13 A schematic diagram of another air conditioning system provided in an embodiment of the present application;

[0029] Figure 14 A schematic diagram of another air conditioning system provided in an embodiment of the present application;

[0030] Figure 15 A schematic diagram of the composition of another air-conditioning system provided in an embodiment of the present application.

[0031] Reference numerals:

[0032] 100. Air-conditioning system; 101. Control unit; 102. Determination unit; 103. Processing module; 1031. Processor; 104. Communication module; 1041. Communication bus; 1042. Communication interface; 105. Storage module; 1051. Memory; 1. Compressor; 11. Inlet port; 111. Inlet pressure sensor; 12. Exhaust port; 121. Exhaust pressure sensor; 122. Exhaust temperature sensor; 2. Reversing assembly; 21. First valve port; 22. Second valve port; 23. Third valve port; 24. Fourth valve port; 3. Indoor heat exchanger; 31. First stop valve; 32. Second stop valve; 4. Outdoor heat exchanger assembly; 41. First part; 411. First part Te temperature sensor; 412. First part temperature sensor; 42. Second part; 421. Second part Te temperature sensor; 422. Second part temperature sensor; 43. First throttle valve; 44. Second throttle valve; 45. First on-off valve; 46. Outdoor fan; 47. Subcooler; 5. Defrost branch; 51. Second on-off valve; 6. Bypass branch; 61. Third throttle valve; 7. Gas-liquid separator; 71. Liquid inlet; 72. Gas outlet; 8. Oil-gas separator; 81. Inlet; 82. Gas discharge port; 83. Oil return capillary; 84. Oil outlet; 9. Outdoor temperature sensor. DETAILED DESCRIPTION

[0033] The embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0034] In the description of the present invention, it should be understood that the terms "center", "up", "down", "front", "back", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0035] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the technical features being referred to. Thus, a feature specified as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0036] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0037] When an air conditioning system is operating in heating mode, frost will form on the outdoor heat exchanger assembly when the ambient temperature and humidity reach certain conditions. In related technologies, air conditioning systems use reverse defrosting to defrost the outdoor heat exchanger assembly. This method reverses the flow of the refrigerant used in heating, supplies the refrigerant discharged from the compressor to the outdoor heat exchanger assembly, and uses the heat from the compressor to defrost the outdoor heat exchanger assembly. During reverse defrosting, the air conditioning system stops heating the room and requires the indoor heat exchanger to absorb some heat from the room, lowering the indoor temperature, severely affecting indoor thermal comfort, and reducing the user experience.

[0038] To address the aforementioned technical issues, the present application provides improvements designed to maintain the indoor heat exchanger's function as a condenser while defrosting the outdoor heat exchanger assembly. Specifically, by configuring the outdoor heat exchanger assembly to include a first portion and a second portion arranged in parallel, the air conditioning system defrosts the first portion using a defrost branch to bypass a portion of the refrigerant from the compressor's exhaust port to the first portion for defrosting. The second portion can then function as an evaporator to maintain the air conditioning system's heating cycle. When defrosting the second portion, the air conditioning system utilizes the latent heat of the high-pressure, medium-temperature refrigerant flowing out of the indoor heat exchanger to defrost the second portion. The first portion can then function as an evaporator to maintain the air conditioning system's heating cycle. This allows the indoor heat exchanger to maintain heating the room while alternately defrosting the first and second portions. This prevents the indoor temperature from being affected by the defrosting process, maintaining a high indoor temperature and improving user comfort. Furthermore, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor's exhaust port is used to defrost the first portion, resulting in a significant defrosting effect. The second section is defrosted using the high-pressure, medium-temperature refrigerant flowing out of the indoor heat exchanger, achieving significant defrosting results. This combined defrosting method of low-pressure sensible heat and high-pressure waste heat not only leverages the advantages of both waste and sensible heat defrosting, but also avoids the significant waste of waste heat defrosting capacity, the poor reliability of sensible heat defrosting, and the limited applicable operating conditions. This, in turn, improves the defrosting speed and reliability of the air conditioning system to a certain extent.

[0039] The air conditioning system according to the embodiment of the present application is described below.

[0040] See also Figure 1 and Figure 2 , Figure 1 This is a schematic diagram of the composition of an air conditioning system provided in the first embodiment of the present application. Figure 2 This is a schematic diagram of the composition of an air conditioning system provided in the second embodiment of the present application. This embodiment of the present application provides an air conditioning system 100, comprising: a compressor 1, a reversing assembly 2, an indoor heat exchanger 3, an outdoor heat exchanger assembly 4, a defrost branch 5, and a bypass branch 6.

[0041] Please continue reading Figure 1 The compressor 1 has an air intake port 11 and an air exhaust port 12. Specifically, the air intake port 11 of the compressor 1 is used to inhale air. The refrigerant enters the compression chamber of the compressor 1 through the air intake port 11 and is compressed to form a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant gas is then discharged from the compressor 1 through the air exhaust port 12 of the compressor 1 and then enters the air-conditioning system 100 for refrigerant circulation.

[0042] Exemplarily, the compressor 1 may be a scroll compressor, a rotary compressor, a screw compressor, or other types of compressors.

[0043] Please continue reading Figure 1 The reversing assembly 2 includes a first valve port 21, a second valve port 22, a third valve port 23, and a fourth valve port 24. The first valve port 21 is connected to the exhaust port 12. The fourth valve port 24 is connected to the intake port 11. The first valve port 21 can be switched to one of the second and third valve ports 22, 23, and the fourth valve port 24 can be switched to the other of the second and third valve ports 22, 23. That is, when the first valve port 21 is in communication with the second valve port 22, the third valve port 23 is in communication with the fourth valve port 24; when the first valve port 21 is in communication with the third valve port 23, the second valve port 22 is in communication with the fourth valve port 24.

[0044] Exemplarily, the reversing assembly 2 may be a four-way reversing valve. The four-way reversing valve may have two states: open and closed. When the four-way reversing valve is powered on, the four-way reversing valve is open, the first valve port 21 is connected to the second valve port 22, and the third valve port 23 is connected to the fourth valve port 24. When the four-way reversing valve is powered off, the four-way reversing valve is closed, the first valve port 21 is connected to the third valve port 23, and the second valve port 22 is connected to the fourth valve port 24. Of course, it is understandable that in other examples, when the four-way reversing valve is powered off, the first valve port 21 is connected to the second valve port 22, and the third valve port 23 is connected to the fourth valve port 24. When the four-way reversing valve is powered on, the first valve port 21 is connected to the third valve port 23, and the second valve port 22 is connected to the fourth valve port 24.

[0045] Please continue reading Figure 1 , the first end of the indoor heat exchanger 3 is connected to the second valve port 22.

[0046] Please continue reading Figure 1 The outdoor heat exchanger assembly 4 includes a first portion 41 and a second portion 42. The first end of the first portion 41 is connected to the third valve port 23. The first end of the second portion 42 is connected to the third valve port 23, with a first on-off valve 45 connected in series therebetween. The first on-off valve 45 can be used to control the on-off connection between the first end of the second portion 42 and the third valve port 23.

[0047] Thus, the first end of the first part 41 can be connected to the third valve port 23, and the connection and disconnection between the second part 42 and the third valve port 23 can be controlled by the first on-off valve 45, which is beneficial to improving the reliability of the air-conditioning system 100.

[0048] Please continue reading Figure 1A first throttle valve 43 is connected between the second end of the first portion 41 and the second end of the indoor heat exchanger 3. The first throttle valve 43 can throttle and reduce the pressure of the refrigerant flowing through it. The first throttle valve 43 can also control the flow between the second end of the first portion 41 and the second end of the indoor heat exchanger 3. In other words, the opening degree of the first throttle valve 43 is adjustable. The first throttle valve 43 can have a fully open state (opening degree is 100%), a fully closed state (opening degree is 0%), and a throttled state (opening degree is between 0-100%). In the fully closed state of the first throttle valve 43, there is no flow between the second end of the first portion 41 and the second end of the indoor heat exchanger 3. In the fully open state and the throttled state of the first throttle valve 43, there is flow between the second end of the first portion 41 and the second end of the indoor heat exchanger 3. In the throttled state, the first throttle valve 43 can throttle and reduce the pressure of the refrigerant flowing through it.

[0049] A second throttle valve 44 is connected between the second end of the second portion 42 and the second end of the indoor heat exchanger 3. The second throttle valve 44 can throttle and reduce the pressure of the refrigerant flowing through it. The second throttle valve 44 can also control the flow between the second end of the second portion 42 and the second end of the indoor heat exchanger 3. In other words, the opening degree of the second throttle valve 44 is adjustable. The second throttle valve 44 can have a fully open state (opening degree 100%), a fully closed state (opening degree 0%), and a throttled state (opening degree between 0-100%). In the fully closed state, there is no flow between the second end of the second portion 42 and the second end of the indoor heat exchanger 3. When the first portion 41 is in the fully open state or the throttled state, there is flow between the second end of the second portion 42 and the second end of the indoor heat exchanger 3. In the throttled state, the second throttle valve 44 can throttle and reduce the pressure of the refrigerant flowing through it.

[0050] Thus, the flow between the second end of the first portion 41 and the second end of the indoor heat exchanger 3 can be controlled by opening and closing the first throttle valve 43. The refrigerant flowing through the first throttle valve 43 can also be throttled and pressure-reduced by controlling the opening degree of the first throttle valve 43. The flow between the second end of the second portion 42 and the second end of the indoor heat exchanger 3 can also be controlled by opening and closing the second throttle valve 44. The refrigerant flowing through the first throttle valve 43 can also be throttled and pressure-reduced by controlling the opening degree of the first throttle valve 43. This helps improve the stability and reliability of the air-conditioning system 100.

[0051] Please continue reading Figure 1The first end of the defrost branch 5 is connected to the exhaust port 12. The second end of the defrost branch 5 is connected to the pipeline between the first throttle valve 43 and the second end of the first portion 41. A second on-off valve 51 is connected in series with the defrost branch 5. The second on-off valve 51 controls the on-off state of the defrost branch 5. It is understood that the second end of the defrost branch 5 is located between the first throttle valve 43 and the second end of the first portion 41. The refrigerant in the defrost branch 5 can bypass the first throttle valve 43 and enter the first portion 41 directly, preventing the first throttle valve 43 from affecting the state of the refrigerant in the defrost branch 5. This ensures that the refrigerant in the defrost branch 5 is in a high-temperature and high-pressure state. In addition, when frost forms on the first portion 41, the second on-off valve 51 can be controlled to open, allowing the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 to enter the first portion 41 along the defrost branch 5, thereby utilizing the sensible heat of the exhaust gas from the compressor 1 to defrost the first portion 41. At the same time, when there is no need to defrost the first part 41, the second on-off valve 51 can be controlled to be closed, so as to prevent the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 from flowing to the defrost branch 5, thereby affecting the normal operation of the air-conditioning system 100, which is beneficial to improving the reliability of the operation of the air-conditioning system 100.

[0052] Please continue reading Figure 1 , the first end of the bypass branch 6 is connected to the first end of the second part 42. The second end of the bypass branch 6 is connected to the pipeline between the first throttle valve 43 and the second end of the first part 41. A third throttle valve 61 is connected in series to the bypass branch 6. The third throttle valve 61 can throttle and reduce the pressure of the refrigerant flowing through it. The third throttle valve 61 can also control the on-off between the first end of the second part 42 and the second end of the first part 41. In other words, the opening of the third throttle valve 61 is adjustable. The third throttle valve 61 can have a fully open state (opening is 100%), a fully closed state (opening is 0) and a throttling state (opening is between 0-100%). In the fully closed state of the third throttle valve 61, there is no conduction between the first end of the second part 42 and the second end of the first part 41. In the fully open state and throttling state of the first part 41 , the first end of the second part 42 is connected to the second end of the first part 41 , and in the throttling state, the third throttle valve 61 can throttle and reduce the pressure of the refrigerant flowing through it.

[0053] The air conditioning system 100 according to the embodiment of the present application has a cooling mode, a heating mode, and a defrost mode. The control process and the flow direction of the refrigerant in the cooling mode, the heating mode, and the defrost mode of the embodiment of the present application are described in detail below.

[0054] Cooling mode

[0055] See also Figure 3 and Figure 4 , Figure 3This is a schematic diagram of the cooling mode of the air-conditioning system provided in the first embodiment of the present application. Figure 4 This is a schematic diagram of the cooling mode of the air conditioning system provided by the second embodiment of the present application. When the air conditioning system 100 is in cooling mode, the first valve port 21 of the reversing assembly 2 is connected to the third valve port 23, the second valve port 22 is connected to the fourth valve port 24, the first on-off valve 45 is open, the second on-off valve 51 is open, the first throttle valve 43 is throttled, the second throttle valve 44 is throttled, and the third throttle valve 61 is fully closed.

[0056] Refrigerant Flow: The high-temperature, high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows through the first valve port 21 into the reversing assembly 2 and out of the reversing assembly 2 through the third valve port 23. The refrigerant flowing out of the third valve port 23 flows into the first and second portions 41 and 42, respectively, where it undergoes sufficient heat exchange, becoming a high-pressure, subcooled liquid refrigerant. The refrigerant flowing out of the first portion 41 then passes through the first throttle valve 43 for throttling and pressure reduction, while the refrigerant flowing out of the second portion 42 passes through the second throttle valve 44 for throttling and pressure reduction. The refrigerant, after throttling and pressure reduction through the first and second throttle valves 43 and 44, flows into the indoor heat exchanger 3, where it undergoes heat exchange and becomes a low-temperature, low-pressure, superheated gaseous refrigerant. Finally, it flows back to the intake port 11 of the compressor 1 through the second and fourth valve ports 22 and 24, respectively, completing the refrigeration cycle of the air conditioning system 100.

[0057] Heating mode

[0058] See also Figure 5 and Figure 6 , Figure 5 This is a schematic diagram of the heating mode of the air-conditioning system provided in the first embodiment of the present application. Figure 6 This is a schematic diagram of the heating mode of the air conditioning system provided by the second embodiment of the present application. When the air conditioning system 100 is in heating mode, the first valve port 21 of the control reversing assembly 2 is connected to the second valve port 22, the third valve port 23 is connected to the fourth valve port 24, the first on-off valve 45 is open, the second on-off valve 51 is disconnected, the first throttle valve 43 is throttled, the second throttle valve 44 is throttled, and the third throttle valve 61 is fully closed.

[0059] Refrigerant Flow: The high-temperature, high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows through the first valve port 21 into the reversing assembly 2 and out of the reversing assembly 2 through the second valve port 22. The refrigerant flowing out of the second valve port 22 flows to the indoor heat exchanger 3, where it undergoes heat exchange and becomes a high-temperature, high-pressure liquid refrigerant. After flowing out of the indoor heat exchanger 3, the refrigerant flows through the first throttle valve 43 and the second throttle valve 44, respectively. After being throttled and reduced in pressure by the first throttle valve 43, the refrigerant flows into the first portion 41, where it evaporates into a low-temperature, low-pressure superheated gaseous refrigerant. After being throttled and reduced in pressure by the second throttle valve 44, the refrigerant flows into the second portion 42, where it evaporates into a low-temperature, low-pressure superheated gaseous refrigerant. Finally, the refrigerant flowing out of the first and second portions 41, 42 flows back to the intake port 11 of the compressor 1 through the third and fourth valve ports 23 and 24, respectively, completing the heating cycle of the air conditioning system 100.

[0060] Defrost mode

[0061] See also Figure 7 and Figure 8 , Figure 7 This is a schematic diagram of the air conditioning system provided in the first embodiment of the present application defrosting the first part. Figure 8 This is a schematic diagram of defrosting the first portion of the air conditioning system according to the second embodiment of the present application. When defrosting the first portion 41, the first valve port 21 of the reversing assembly 2 is connected to the second valve port 22, the third valve port 23 is connected to the fourth valve port 24, the first throttle valve 43 is fully closed, the second throttle valve 44 is throttled, the first on-off valve 45 is opened, the second on-off valve 51 is opened, and the third throttle valve 61 is fully closed.

[0062] Refrigerant Flow: The high-temperature, high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows to the reversing assembly 2 and the defrost branch 5, respectively. The refrigerant flowing to the reversing assembly 2 flows through the first valve port 21 and exits the reversing assembly 2 through the second valve port 22. The refrigerant exiting the second valve port 22 flows to the indoor heat exchanger 3. After sufficient heat exchange within the indoor heat exchanger 3, the high-temperature, high-pressure gaseous refrigerant flowing to the indoor heat exchanger 3 is condensed into a high-temperature, high-pressure subcooled liquid refrigerant. After exiting the indoor heat exchanger 3, it flows to the second throttle valve 44, where it is throttled to a low-temperature, low-pressure two-phase refrigerant. It then flows to the second portion 42, where it evaporates into a low-temperature, low-pressure superheated gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant flowing to the defrost branch 5 flows into the first portion 41, where the sensible heat of the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 is used to remove frost from the first portion 41. The refrigerant flowing out of the first part 41 and the refrigerant flowing out of the second part 42 flow back to the suction port 11 of the compressor 1 through the third valve port 23 and the fourth valve port 24 in sequence, thereby completing the defrosting refrigerant cycle for the first part 41.

[0063] See also Figure 9 and Figure 10 , Figure 9 This is a schematic diagram of the air conditioning system provided in the first embodiment of the present application defrosting the second part. Figure 10 This is a schematic diagram of the air conditioning system defrosting the second portion according to the second embodiment of the present application. When defrosting the second portion 42, the first valve port 21 of the reversing assembly 2 is controlled to communicate with the second valve port 22, and the third valve port 23 is controlled to communicate with the fourth valve port 24. The first throttle valve 43 is fully closed, the second throttle valve 44 is fully open, the first on-off valve 45 is fully closed, the second on-off valve 51 is closed, and the third throttle valve 61 is throttled.

[0064] Refrigerant flow direction: The high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows into the reversing component 2 through the first valve port 21, and flows out of the reversing component 2 through the second valve port 22. The refrigerant flowing out of the second valve port 22 flows to the indoor heat exchanger 3. The high-temperature and high-pressure gaseous refrigerant does not undergo complete heat exchange in the indoor heat exchanger 3. After the heat exchange, it becomes a high-temperature and high-pressure subcooled liquid refrigerant or a two-phase refrigerant with a small degree of subcooling. After flowing out of the indoor heat exchanger 3, it flows to the second throttle valve 44, and after passing through the second throttle valve 44, it flows to the second part 42. Then, the waste heat of the high-temperature and high-pressure subcooled liquid refrigerant (the waste heat is sensible heat) or the high-temperature and high-pressure two-phase refrigerant (the waste heat is sensible heat plus latent heat) flowing out of the indoor heat exchanger 3 is utilized. The second part 42 is defrosted, and the refrigerant after defrosting in the second part 42 flows to the bypass branch 6, and then flows to the third throttle valve 61 on the bypass branch 6. After throttling and reducing the pressure by the third throttle valve 61, it becomes a low-temperature and low-pressure two-phase refrigerant, and then flows into the first part 41 again, and evaporates into a low-temperature and low-pressure superheated gaseous refrigerant in the first part 41. Finally, the refrigerant flowing out of the first part 41 flows back to the intake port 11 of the compressor 1 through the third valve port 23 and the fourth valve port 24 in turn, thereby completing the defrosting refrigerant cycle for the second part 42.

[0065] Thus, the defrost branch 5 can bypass a portion of the refrigerant from the exhaust port 12 of the compressor 1 to the first portion 41 for defrosting, and the high-pressure, medium-temperature refrigerant flowing out of the indoor heat exchanger 3 can be used to defrost the second portion 42. This allows the first portion 41 and the second portion 42 to be defrosted alternately while maintaining the indoor heating state of the indoor heat exchanger 3. Furthermore, during the switching process between heating and defrosting, the reversing assembly 2 does not reverse, thereby extending the service life of the reversing assembly 2.

[0066] Please continue reading Figure 9 , the first portion 41 may be located directly above the second portion 42. Figure 10As shown, the first portion 41 may also be located directly below the second portion 42. Thus, the defrost branch 5 and the bypass branch 6 can be reasonably arranged, which is beneficial to reducing costs.

[0067] Please continue reading Figure 9 The second end of the bypass branch 6 is connected to the pipeline between the second end of the defrost branch 5 and the second end of the first portion 41. This arrangement can prevent the defrost branch 5 from affecting the bypass branch 6, which is beneficial to improving the reliability of the air conditioning system 100. On the other hand, the position of the bypass branch 6 can be reasonably set.

[0068] In other embodiments, see Figure 10 The second end of the bypass branch 6 is connected to the pipeline between the second end of the defrost branch 5 and the first throttle valve 43. Therefore, the position of the bypass branch 6 can be reasonably set.

[0069] See also Figure 9 The first throttle valve 43, the second throttle valve 44, and the third throttle valve 61 may be electronic expansion valves. This configuration can improve the operating speed and accuracy of the air conditioning system 100. In other embodiments, the first throttle valve 43, the second throttle valve 44, and the third throttle valve 61 may also be thermal expansion valves.

[0070] In some embodiments, the first portion 41 and the second portion 42 can be divided into two independent heat exchangers. This prevents the air conditioning system 100 from ceasing to operate if one of the first portion 41 and the second portion 42 is damaged when the air conditioning system 100 is in cooling or heating mode, thereby improving the stability and reliability of the air conditioning system 100.

[0071] In other embodiments, the first portion 41 and the second portion 42 may also be divided into two parts of the same heat exchanger. This arrangement facilitates the assembly of the air conditioning system 100, thereby improving the assembly efficiency of the air conditioning system 100.

[0072] In some embodiments, the first on-off valve 45 may be a two-way valve, which is advantageous in improving the response speed and reliability of the air conditioning system 100.

[0073] In some embodiments, the second on-off valve 51 may be a solenoid valve, which is advantageous in improving the response speed and reliability of the air conditioning system 100.

[0074] In other embodiments, the second on-off valve 51 may also be an electronic expansion valve.

[0075] Please continue reading Figure 9The first throttle valve 43 and the second throttle valve 44 are connected to the second end of the indoor heat exchanger 3 via a common subcooler 47. The provision of the subcooler 47 can reduce the flash gas generated during the throttling process of the air-conditioning system 100, thereby improving the cooling capacity of the air-conditioning system 100 and the operating stability of the compressor 1, thereby improving the stability and reliability of the air-conditioning system 100.

[0076] Please continue reading Figure 1 The first end of the indoor heat exchanger 3 is connected to a first shutoff valve 31, and the second end of the indoor heat exchanger 3 is connected to a second shutoff valve 32. Thus, the provision of the first shutoff valve 31 and the second shutoff valve 32 facilitates maintenance and repair of the air conditioning system 100. Specifically, when the indoor heat exchanger 3 needs to be repaired or replaced, the first shutoff valve 31 and the second shutoff valve 32 can be closed, making it easier to repair the indoor heat exchanger 3 without having to drain the refrigerant from the entire air conditioning system 100.

[0077] For example, the air conditioning system 100 may be a multi-split system. The air conditioning system 100 includes multiple indoor units. Each indoor unit is equipped with an indoor heat exchanger 3. The multiple indoor units are arranged in parallel. The first ends of the indoor heat exchangers 3 of the multiple indoor units may be connected to a first shut-off valve 31. The second ends of the indoor heat exchangers 3 of the multiple indoor units may be connected to a second shut-off valve 32. Of course, it is understood that in other examples, the air conditioning system 100 may include only one indoor unit.

[0078] Please continue reading Figure 1 In some embodiments, the air conditioning system 100 further includes a gas-liquid separator 7. The gas-liquid separator 7 is disposed between the compressor 1 and the reversing assembly 2. The gas-liquid separator 7 has a liquid inlet 71 and a gas outlet 72. The liquid inlet 71 is connected to the fourth valve port 24. The gas outlet 72 is connected to the air intake 11. By providing a gas-liquid separator, the refrigerant entering the compressor 1 can be separated into gas and liquid, thereby avoiding liquid hammer problems in the compressor 1 and thus facilitating the protection of the compressor 1.

[0079] Please continue reading Figure 1 In some embodiments, the air conditioning system 100 further includes an oil-gas separator 8. The oil-gas separator 8 is disposed between the compressor 1 and the reversing assembly 2. The oil-gas separator 8 has an inlet 81, a gas discharge port 82, and an oil outlet 84. The inlet 81 is connected to the exhaust port 12. The gas discharge port 82 is connected to the first valve port 21. The oil outlet 84 is connected to the intake port 11. The provision of the oil-gas separator 8 can enhance the protection of the compressor 1, thereby improving the stability and reliability of the air conditioning system 100.

[0080] Please continue reading Figure 1In some embodiments, the air conditioning system 100 further includes an oil return capillary tube 83. The oil return capillary tube 83 is located between the compressor 1 and the oil outlet 84 of the oil-gas separator 8. The oil return capillary tube 83 can return the liquid separated in the oil-gas separator 8 to the air intake 11 of the compressor 1.

[0081] Please continue reading Figure 1 In some embodiments, an outdoor fan 46 may be provided on one side of the outdoor heat exchanger assembly. This arrangement can improve the heat exchange efficiency of the outdoor heat exchanger assembly 4.

[0082] Based on the structure of the air conditioning system 100 described above, there are two defrosting methods for the air conditioning system 100 according to the embodiment of the present application.

[0083] See also Figure 11 , Figure 11 This is a flow chart of a first defrost control method for an air conditioning system provided in an embodiment of the present application. The defrost control method for the air conditioning system 100 includes the following steps:

[0084] S1: When the air conditioning system 100 is operating in the heating mode, it is determined whether the air conditioning system 100 meets the defrost conditions. When the air conditioning system 100 is in the heating mode, the first valve port 21 of the reversing assembly 2 is in communication with the second valve port 22, the third valve port 23 is in communication with the fourth valve port 24, the first on-off valve 45 is open, the second on-off valve 51 is open, the first throttle valve 43 is throttled, the second throttle valve 44 is throttled, and the third throttle valve 61 is fully closed.

[0085] S2: If the air-conditioning system 100 meets the defrosting condition, the first throttle valve 43 is controlled to be fully closed, and the second on-off valve 51 is opened, so that the air-conditioning system 100 runs the first defrosting mode to defrost the first part 41.

[0086] Thus, in the first defrost mode, the first valve port 21 and the second valve port 22 of the reversing assembly 2 are kept in communication, the third valve port 23 and the fourth valve port 24 are kept in communication, the first throttle valve 43 is fully closed, the second throttle valve 44 is throttled, the first on-off valve 45 is opened, the second on-off valve 51 is opened, and the third throttle valve 61 is fully closed. At this time, the flow direction of the refrigerant in the first defrost mode can be: the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows to the reversing assembly 2 and the defrost branch 5 respectively. The refrigerant flowing to the reversing assembly 2 flows into the reversing assembly 2 through the first valve port 21 and flows out of the reversing assembly 2 from the second valve port 22. The refrigerant flowing out of the second valve port 22 flows to the indoor heat exchanger 3. The high-temperature, high-pressure gaseous refrigerant flowing to the indoor heat exchanger 3 undergoes sufficient heat exchange within the indoor heat exchanger 3 and is condensed into a high-temperature, high-pressure subcooled liquid refrigerant. It then flows out of the indoor heat exchanger 3 and flows to the second throttle valve 44. After being throttled by the second throttle valve 44, it becomes a low-temperature, low-pressure two-phase refrigerant. It then flows to the second portion 42, where it evaporates and becomes a low-temperature, low-pressure superheated gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant flowing to the defrost branch 5 flows into the first portion 41, where the sensible heat of the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 is used to remove frost from the first portion 41. The refrigerant flowing out of the first portion 41 and the refrigerant flowing out of the second portion 42 flow back to the intake port 11 of the compressor 1 through the third valve port 23 and the fourth valve port 24, respectively.

[0087] S3: Determine whether the air-conditioning system 100 meets the first defrost mode end condition.

[0088] S4: If the air-conditioning system meets the end conditions of the first defrost mode, the second throttle valve 44 is controlled to be fully open, the first on-off valve 45 is closed, the second on-off valve 51 is closed, and the third throttle valve 61 is throttled to control the air-conditioning system 100 to exit the first defrost mode and run the second defrost mode. In the second defrost mode, the second part 42 is defrosted.

[0089] Thus, in the second defrost mode, the first valve port 21 and the second valve port 22 of the reversing assembly 2 are kept in communication, the third valve port 23 and the fourth valve port 24 are kept in communication, the first throttle valve 43 is fully closed, the second throttle valve 44 is fully open, the first on-off valve 45 is closed, the second on-off valve 51 is closed, and the third throttle valve 61 is throttled. At this time, the flow direction of the refrigerant in the second defrost mode can be: the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows into the reversing assembly 2 through the first valve port 21 and flows out of the reversing assembly 2 through the second valve port 22. The refrigerant flowing out of the second valve port 22 flows to the indoor heat exchanger 3. The high-temperature and high-pressure gaseous refrigerant does not undergo complete heat exchange in the indoor heat exchanger 3. After heat exchange, it becomes a high-temperature and high-pressure subcooled liquid refrigerant or a two-phase refrigerant with a small degree of subcooling. After flowing out of the indoor heat exchanger 3, it flows to the second throttle valve 44. After passing through the second throttle valve 44, it flows to the second part 42. Then, the high-temperature and high-pressure subcooled liquid refrigerant (the waste heat is sensible heat) or the high-temperature and high-pressure two-phase refrigerant (the waste heat is The waste heat (sensible heat plus latent heat) of the second part 42 is used to defrost the second part 42. After the defrost of the second part 42, the refrigerant flows to the bypass branch 6, and then flows to the third throttle valve 61 on the bypass branch 6. After throttling and reducing the pressure by the third throttle valve 61, it becomes a low-temperature and low-pressure two-phase refrigerant, and then flows into the first part 41 again, and evaporates into a low-temperature and low-pressure superheated gaseous refrigerant in the first part 41. Finally, the refrigerant flowing out of the first part 41 flows back to the suction port 11 of the compressor 1 through the third valve port 23 and the fourth valve port 24 in sequence.

[0090] S5: Determine whether the air conditioning system 100 meets the second defrost mode end condition.

[0091] S6: If the end condition of the second defrost mode is met, the first throttle valve 43 and the second throttle valve 44 are controlled to throttle, the first on-off valve 45 is opened, the second on-off valve 51 is closed, and the third throttle valve 61 is closed to exit the second defrost mode and run the heating mode.

[0092] As a result, when switching from the heating mode to the first defrost mode and the second defrost mode for defrosting the first part 41 and the second part 42, the reversing assembly 2 never reverses, which can reduce the power consumption of the air-conditioning system 100, and the air-conditioning system 100 can achieve uninterrupted heating, so that the indoor temperature can always be kept high, which is beneficial to improving the user's comfort. At the same time, the first defrost mode uses the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 to defrost the first part 41, and the defrosting effect is significant. The second defrost mode uses the high-pressure and medium-temperature refrigerant flowing out of the indoor heat exchanger 3 to defrost the second part 42. The defrosting method that combines low-pressure sensible heat with high-pressure waste heat can not only utilize the advantages of waste heat defrosting and sensible heat defrosting, but also avoid the serious waste of waste heat defrosting capacity, poor reliability of sensible heat defrosting, and narrow applicable working conditions. It is beneficial to improve the reliability and stability of the operation of the air-conditioning system 100. In addition, when the first part 41 is located directly above the second part 42, during the defrosting process of the outdoor heat exchanger assembly 4, by first defrosting the first part 41 and then defrosting the second part 42 after the defrosting of the first part 41 is completed, it is beneficial to ensure the defrosting effect of the outdoor heat exchanger assembly 4 and prevent the problem that the second part 42 is frozen when the defrosted water droplets from the first part 41 fall onto the second part 42 serving as the evaporator, resulting in a deterioration in the defrosting effect of the second part 42.

[0093] In some embodiments, to improve the evaporation capacity of the first portion 41, an outdoor fan 46 is disposed on a side of the first portion 41 away from the second portion 42. In step S4, if the air conditioning system meets the first defrost mode termination condition, the outdoor fan 46 is controlled to turn on, thereby supplying air to the first portion 41. Thus, after defrosting the first portion 41, turning on the outdoor fan 46 can improve the evaporation capacity of the first portion 41, thereby increasing the suction pressure of the compressor 1. This allows for rapid air delivery to the indoor space after the air conditioning system 100 completes defrosting, thereby improving the user experience.

[0094] In some embodiments, before determining that the air conditioning system 100 meets the defrost conditions, the outdoor ambient temperature Ta, the temperature Te1 at the second end of the first portion 41, and the temperature Te2 at the second end of the second portion 42 are obtained. If Ta ≤ a, Te1 / Te2 ≤ b, and the air conditioning system 100 has been operating in heating mode for a first predetermined duration, the air conditioning system is determined to meet the defrost conditions. This allows the air conditioning system 100 to accurately determine whether to defrost, improving the sensitivity and reliability of the defrost operation of the air conditioning system 100.

[0095] For example, in Figure 10In the described embodiment, an outdoor temperature sensor 9 can be set on the outside of the air-conditioning system 100 to obtain the outdoor ambient temperature Ta, a first part Te temperature sensor 411 can be set at the second end of the first part 41 to obtain the temperature Te1 of the second end of the first part 41, and a second part Te temperature sensor 421 can be set at the second end of the second part 42 to obtain the temperature Te2 of the second end of the second part 42.

[0096] In some embodiments, -7°C < a < 7°C. For example, the threshold a of the outdoor ambient temperature Ta may be -6°C, -5°C, -4°C, -3°C, -2°C, -1°C, 0°C, 1°C, 2°C, 3°C, 4°C, 5°C, or 6°C.

[0097] In some embodiments, -5°C ≤ b ≤ 0°C. For example, the ratio of Te1 / Te2 may be -5°C, -4°C, -3°C, -2°C, -1°C, or 0°C.

[0098] In some embodiments, the first set time length is ≥ 10 minutes. For example, the first set time length may be 10 minutes, 11 minutes, 12 minutes, 13 minutes, or 14 minutes.

[0099] In some embodiments, the first defrost mode terminates when the temperature Te1 at the second end of the first portion 41 exceeds f and persists for a first predetermined time. This allows the system to exit the first defrost mode promptly when the first defrost mode termination condition is met, thereby improving the intelligence and reliability of the air conditioning system 100.

[0100] In some embodiments, the second defrost mode terminates when the temperature Te2 at the second end of the second portion 42 exceeds f and persists for a first predetermined time. This allows the system to exit the second defrost mode promptly when the second defrost mode termination condition is met, thereby improving the intelligence and reliability of the air conditioning system 100.

[0101] In some embodiments, 10° C. ≤ f ≤ 25° C. For example, the temperature f at the second end of the second portion 42 may be 10° C., 11° C., 12° C., 13° C., 14° C., 15° C., 16° C., 17° C., 18° C., 19° C., 20° C., 21° C., 22° C., 23° C., 24° C., or 25° C.

[0102] In some embodiments, 5 seconds ≤ the first preset time ≤ 30 seconds. For example, the first preset time may be 5 seconds, 10 seconds, 15 seconds, 20 seconds, 25 seconds, or 30 seconds.

[0103] In some embodiments, the opening of the second throttle valve 44 is adjustable. When defrosting the first portion 41, the opening of the second throttle valve 44 is adjusted to meet a first preset condition. The first preset condition is: the suction superheat of the compressor 1 satisfies: Tssh ≥ d, and the exhaust superheat of the compressor 1 satisfies: Tdsh ≥ e; wherein Tssh = Tg2 - Tc_ps, where Tg2 is the temperature of the first end of the second portion 42, and Tc_ps is the saturation temperature corresponding to the suction pressure Ps at the intake port 11. This setting can improve the accuracy of the opening control of the second throttle valve 44, thereby helping to improve the reliability of the air conditioning system 100. It should be noted that Tdsh = Td - Tc_pd, where Td is the temperature of the exhaust port 12 of the compressor 1, and Tc_pd is the saturation temperature corresponding to the exhaust pressure Pd at the exhaust port 12.

[0104] For example, in Figure 10 In the embodiment described, a second portion temperature sensor 422 may be provided at the first end of the second portion 42 to obtain a temperature Tg2 at the first end of the second portion 42. A suction pressure sensor 111 may be provided at the suction port 11 of the compressor 1 to detect the suction pressure Ps. A discharge pressure sensor 121 may be provided at the discharge port 12 of the compressor 1 to detect the discharge pressure Pd. An discharge temperature sensor 122 may be provided at the discharge port 12 of the compressor 1 to detect the discharge temperature Td.

[0105] In some embodiments, the opening of the third throttle valve 61 is adjustable. When defrosting the second portion 42, the opening of the third throttle valve 61 is adjusted to meet a second preset condition. The second preset condition is that the suction superheat of the compressor 1 satisfies: Tssh ≥ d, and the discharge superheat of the compressor 1 satisfies: Tdsh ≥ e. Here, Tssh = Tg1 - Tc_ps, where Tg1 is the temperature at the first end of the first portion 41, and Tc_ps is the saturation temperature corresponding to the suction pressure Ps at the suction port 11.

[0106] For example, in Figure 10 In the embodiment, a first portion temperature sensor 412 may be provided at the first end of the first portion 41 to obtain the temperature Tg1 of the first end of the first portion 41 .

[0107] In some embodiments, 0° C. ≤ d ≤ 10° C. For example, the value of d can be 0° C., 1° C., 2° C., 3° ​​C., 4° C., 5° C., 6° C., 7° C., 8° C., 9° C., or 10° C.

[0108] In some embodiments, 20° C. ≤ e ≤ 40° C. For example, the value of e can be 20° C., 25° C., 30° C., 35° C., or 40° C.

[0109] In some embodiments, when defrosting the second portion 42, the indoor fan of the air conditioning system 100 is controlled to stop running or run at the lowest wind speed. This configuration ensures that the refrigerant flowing into the second portion 42 has residual heat in the second defrost mode, thereby ensuring the defrosting efficiency of the second portion 42.

[0110] The defrost control method of the air-conditioning system 100 according to the second embodiment of the present application is described below.

[0111] See also Figure 12 , Figure 12 This is a flow chart of a second defrost control method for an air conditioning system provided in an embodiment of the present application. The defrost control method for the air conditioning system 100 includes the following steps:

[0112] S1: When the air conditioning system 100 is operating in the heating mode, it is determined whether the air conditioning system 100 meets the defrost conditions. When the air conditioning system 100 is in the heating mode, the first valve port 21 of the reversing assembly 2 is in communication with the second valve port 22, the third valve port 23 is in communication with the fourth valve port 24, the first on-off valve 45 is open, the second on-off valve 51 is open, the first throttle valve 43 is throttled, the second throttle valve 44 is throttled, and the third throttle valve 61 is fully closed.

[0113] S2: If the air-conditioning system 100 meets the defrosting conditions, the first throttle valve 43 is controlled to be fully closed, the second throttle valve 44 is fully opened, the first on-off valve 45 is closed, and the third throttle valve 61 is throttled, so that the air-conditioning system 100 runs the first defrosting mode and defrosts the second part 42.

[0114] Thus, in the first defrost mode, the first valve port 21 and the second valve port 22 of the reversing assembly 2 are maintained in communication, the third valve port 23 and the fourth valve port 24 are maintained in communication, the first throttle valve 43 is fully closed, the second throttle valve 44 is fully open, the first on-off valve 45 is fully closed, the second on-off valve 51 is closed, and the third throttle valve 61 is throttled. At this time, the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows into the reversing assembly 2 through the first valve port 21 and flows out of the reversing assembly 2 through the second valve port 22. The refrigerant flowing out of the second valve port 22 flows to the indoor heat exchanger 3. The high-temperature and high-pressure gaseous refrigerant does not undergo complete heat exchange in the indoor heat exchanger 3. After heat exchange, it becomes a high-temperature and high-pressure subcooled liquid refrigerant or a two-phase refrigerant with a small degree of subcooling. After flowing out of the indoor heat exchanger 3, it flows to the second throttle valve 44, and then flows to the second part 42 after passing through the second throttle valve 44. Then, the high-temperature and high-pressure subcooled liquid refrigerant (the waste heat is sensible heat) or the high-temperature and high-pressure two-phase refrigerant (the waste heat is sensible heat) flowing out of the indoor heat exchanger 3 is used. The second part 42 is defrosted by the waste heat (sensible heat plus latent heat). After the defrost of the second part 42, the refrigerant flows to the bypass branch 6, and then flows to the third throttle valve 61 on the bypass branch 6. After throttling and reducing the pressure by the third throttle valve 61, it becomes a low-temperature and low-pressure two-phase refrigerant, and then flows into the first part 41 again, and evaporates into a low-temperature and low-pressure superheated gaseous refrigerant in the first part 41. Finally, the refrigerant flowing out of the first part 41 passes through the third valve port 23 and the fourth valve port 24 in sequence and flows back to the suction port 11 of the compressor 1.

[0115] S3: Determine whether the air-conditioning system 100 meets the first defrost mode end condition.

[0116] S4: If the air-conditioning system meets the end conditions of the first defrost mode, the second throttle valve 44 is controlled to throttle, the first on-off valve 45 is opened, the second on-off valve 51 is opened, and the third throttle valve 61 is fully closed to control the air-conditioning system 100 to exit the first defrost mode and run the second defrost mode. In the second defrost mode, the first part 41 is defrosted.

[0117] Thus, in the second defrost mode, the first valve port 21 of the reversing assembly 2 is kept in communication with the second valve port 22, the third valve port 23 is kept in communication with the fourth valve port 24, the first throttle valve 43 is fully closed, the second throttle valve 44 is throttled, the first on-off valve 45 is opened, the second on-off valve 51 is opened, and the third throttle valve 61 is fully closed. At this time, the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 flows to the reversing assembly 2 and the defrost branch 5 respectively. The refrigerant flowing to the reversing assembly 2 flows into the reversing assembly 2 through the first valve port 21 and flows out of the reversing assembly 2 from the second valve port 22. The refrigerant flowing out of the second valve port 22 flows to the indoor heat exchanger 3. The high-temperature, high-pressure gaseous refrigerant flowing to the indoor heat exchanger 3 undergoes sufficient heat exchange within the indoor heat exchanger 3 and is condensed into a high-temperature, high-pressure subcooled liquid refrigerant. It then flows out of the indoor heat exchanger 3 and flows to the second throttle valve 44. After being throttled by the second throttle valve 44, it becomes a low-temperature, low-pressure two-phase refrigerant. It then flows to the second portion 42, where it evaporates and becomes a low-temperature, low-pressure superheated gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant flowing to the defrost branch 5 flows into the first portion 41, where the sensible heat of the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 is used to remove frost from the first portion 41. The refrigerant flowing out of the first portion 41 and the refrigerant flowing out of the second portion 42 flow back to the intake port 11 of the compressor 1 through the third valve port 23 and the fourth valve port 24, respectively.

[0118] S5: Determine whether the air conditioning system 100 meets the second defrost mode end condition.

[0119] S6: If the end condition of the second defrost mode is met, the first throttle valve 43 and the second throttle valve 44 are controlled to throttle, the first on-off valve 45 is opened, the second on-off valve 51 is closed, and the third throttle valve 61 is closed to exit the second defrost mode and run the heating mode.

[0120] As a result, when switching from the heating mode to the first defrost mode and the second defrost mode for defrosting the first part 41 and the second part 42, the reversing assembly 2 remains in the same direction, which can reduce the power consumption of the air conditioning system 100. The air conditioning system 100 can also achieve uninterrupted heating, which can keep the indoor temperature at a high level, thereby improving user comfort. At the same time, the second defrost mode uses the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port 12 of the compressor 1 to defrost the first part 41, and the defrosting effect is significant. The first defrost mode uses the high-pressure and medium-temperature refrigerant flowing out of the indoor heat exchanger 3 to defrost the second part 42. By combining low-pressure sensible heat with high-pressure waste heat, the defrosting method not only utilizes the advantages of waste heat defrosting and sensible heat defrosting, but also avoids the serious waste of waste heat defrosting capacity, the poor reliability of sensible heat defrosting, and the narrow applicable working conditions, thereby improving the reliability and stability of the operation of the air conditioning system 100. In addition, when the second part 42 is located directly above the first part 41, during the defrosting process of the outdoor heat exchanger assembly 4, by first defrosting the second part 42 and then defrosting the first part 41 after the defrosting of the second part 42 is completed, it is beneficial to ensure the defrosting effect of the outdoor heat exchanger assembly 4 and prevent the problem that the first part 41 is frozen when the defrosted water droplets from the second part 42 fall onto the first part 41 serving as the evaporator, resulting in a deterioration in the defrosting effect of the first part 41.

[0121] In some embodiments, to improve the evaporation capacity of the second portion 42, an outdoor fan 46 is disposed on a side of the second portion 42 away from the first portion 41. In step S4, if the air conditioning system meets the first defrost mode termination condition, the outdoor fan 46 is controlled to turn on, thereby supplying air to the second portion 42. Thus, after defrosting the second portion 42, turning on the outdoor fan 46 can improve the evaporation capacity of the second portion 42, thereby increasing the suction pressure of the compressor 1. This allows for rapid air delivery to the indoor space after the air conditioning system 100 completes defrosting, thereby improving the user experience.

[0122] In some embodiments, before determining that the air conditioning system 100 meets the defrost conditions, the outdoor ambient temperature Ta, the temperature Te1 at the second end of the first portion 41, and the temperature Te2 at the second end of the second portion 42 are obtained. If Ta ≤ a, Te1 / Te2 ≤ b, and the air conditioning system 100 has been operating in heating mode for a first predetermined time, the air conditioning system is determined to meet the defrost conditions. This allows the air conditioning system 100 to prepare for defrosting, improving the sensitivity and reliability of the defrost process.

[0123] For example, in Figure 10In the described embodiment, an outdoor temperature sensor 9 can be set on the outside of the air-conditioning system 100 to obtain the outdoor ambient temperature Ta, a first part Te temperature sensor 411 can be set at the second end of the first part 41 to obtain the temperature Te1 of the second end of the first part 41, and a second part Te temperature sensor 421 can be set at the second end of the second part 42 to obtain the temperature Te2 of the second end of the second part 42.

[0124] In some embodiments, -7°C < a < 7°C. For example, the threshold a of the outdoor ambient temperature Ta may be -6°C, -5°C, -4°C, -3°C, -2°C, -1°C, 0°C, 1°C, 2°C, 3°C, 4°C, 5°C, or 6°C.

[0125] In some embodiments, -5°C ≤ b ≤ 0°C. For example, the ratio of Te1 / Te2 may be -5°C, -4°C, -3°C, -2°C, -1°C, or 0°C.

[0126] In some embodiments, the first set time length is ≥ 10 minutes. For example, the first set time length may be 10 minutes, 11 minutes, 12 minutes, 13 minutes, or 14 minutes.

[0127] In some embodiments, the first defrost mode terminates when the temperature Te2 at the second end of the second portion 42 exceeds f and persists for a first predetermined time. Thus, the first defrost mode can be promptly exited when the first defrost mode termination condition is met, thereby improving the intelligence and reliability of the air conditioning system 100.

[0128] In some embodiments, the second defrost mode terminates when the temperature Te1 at the second end of the first portion 41 exceeds f and persists for a first predetermined time. This allows the system to exit the second defrost mode promptly when the second defrost mode termination condition is met, thereby improving the intelligence and reliability of the air conditioning system 100.

[0129] In some embodiments, 10° C. ≤ f ≤ 25° C. For example, the temperature f at the second end of the second portion 42 may be 10° C., 11° C., 12° C., 13° C., 14° C., 15° C., 16° C., 17° C., 18° C., 19° C., 20° C., 21° C., 22° C., 23° C., 24° C., or 25° C.

[0130] In some embodiments, 5 seconds ≤ the first preset time ≤ 30 seconds. For example, the first preset time may be 5 seconds, 10 seconds, 15 seconds, 20 seconds, 25 seconds, or 30 seconds.

[0131] In some embodiments, the opening of the second throttle valve 44 is adjustable. When defrosting the first portion 41, the opening of the second throttle valve 44 is adjusted to meet a first preset condition. The first preset condition is: the suction superheat of the compressor 1 satisfies: Tssh ≥ d, and the exhaust superheat of the compressor 1 satisfies: Tdsh ≥ e; wherein Tssh = Tg2 - Tc_ps, where Tg2 is the temperature of the first end of the second portion 42, and Tc_ps is the saturation temperature corresponding to the suction pressure Ps at the intake port 11. This setting can improve the accuracy of the opening control of the second throttle valve 44, thereby helping to improve the reliability of the air conditioning system 100. It should be noted that Tdsh = Td - Tc_pd, where Td is the temperature of the exhaust port 12 of the compressor 1, and Tc_pd is the saturation temperature corresponding to the exhaust pressure Pd at the exhaust port 12.

[0132] For example, in Figure 10 In the described embodiment, a second part temperature sensor 422 can be set at the first end of the second part 42 to obtain the temperature Tg2 of the first end of the second part 42, an intake pressure sensor 111 can be set at the intake port 11 of the compressor 1 to detect the intake pressure Ps, and an exhaust pressure sensor 121 and an exhaust temperature sensor 122 can be set at the exhaust port 12 of the compressor 1 to detect the exhaust pressure Pd and the exhaust temperature Td.

[0133] In some embodiments, the opening of the third throttle valve 61 is adjustable. When defrosting the second portion 42, the opening of the third throttle valve 61 is adjusted to meet a second preset condition. The second preset condition is that the suction superheat of the compressor 1 satisfies: Tssh ≥ d, and the discharge superheat of the compressor 1 satisfies: Tdsh ≥ e. Here, Tssh = Tg1 - Tc_ps, where Tg1 is the temperature at the first end of the first portion 41, and Tc_ps is the saturation temperature corresponding to the suction pressure Ps at the suction port 11.

[0134] For example, in Figure 10 In the embodiment, a first portion temperature sensor 412 may be provided at the first end of the first portion 41 to obtain the temperature Tg1 of the first end of the first portion 41 .

[0135] In some embodiments, 0° C. ≤ d ≤ 10° C. For example, the value of d can be 0° C., 1° C., 2° C., 3° ​​C., 4° C., 5° C., 6° C., 7° C., 8° C., 9° C., or 10° C.

[0136] In some embodiments, 20° C. ≤ e ≤ 40° C. For example, the value of e can be 20° C., 25° C., 30° C., 35° C., or 40° C.

[0137] In some embodiments, when defrosting the second portion 42, the indoor fan of the air conditioning system 100 is controlled to stop running or run at the lowest wind speed. This configuration ensures that the refrigerant flowing into the second portion 42 has residual heat in the second defrost mode, thereby ensuring the defrosting efficiency of the second portion 42.

[0138] The above mainly introduces the solution provided by the embodiment of the present invention from the perspective of the air-conditioning system 100. It can be understood that in order to realize the above functions, the air-conditioning system 100 includes hardware structures and / or software modules corresponding to the execution of each function. It should be easily appreciated by those skilled in the art that, in combination with the algorithm steps of each example described in the embodiments disclosed herein, the present invention can be implemented in the form of hardware or a combination of hardware and computer software. Whether a function is executed in the form of hardware or computer software driving hardware depends on the specific application and design constraints of the technical solution. Professional and technical personnel can use different methods to implement the described functions for each specific application, but such implementation should not be considered to exceed the scope of the present invention.

[0139] In embodiments of the present invention, the air conditioning system 100 can be divided into functional modules based on the above-described method example. For example, each functional module can be divided into corresponding functional modules, or two or more functions can be integrated into a single processing module 103. These integrated modules can be implemented as either hardware or software functional modules. It should be noted that the module division in the embodiments of the present invention is illustrative and represents only one logical functional division. In actual implementation, other division methods may be used.

[0140] In the case of dividing each functional module into corresponding functional modules, Figure 13 Another possible schematic diagram of the air conditioning system involved in the above embodiment is shown. Figure 13 As shown, the air conditioning system 100 may include: a control unit 101 and a determination unit 102 .

[0141] The control unit 101 is used to support the air-conditioning system 100 in executing the steps of the control method of the air-conditioning system 100 shown in the figure.

[0142] The determining unit 102 is configured to support the air-conditioning system 100 in executing the steps of the control method of the air-conditioning system 100 .

[0143] It should be noted that all relevant contents of each step involved in the above method embodiment can be referred to the functional description of the corresponding functional module and will not be repeated here.

[0144] The air-conditioning system 100 provided in the embodiment of the present invention is used to execute the control method of the air-conditioning system 100 described above, and thus can achieve the same effect as the control method of the air-conditioning system 100 described above.

[0145] In the case of an integrated unit, Figure 14 FIG. 1 shows another possible schematic diagram of the air conditioning system involved in the above embodiment. Figure 14 As shown, the air conditioning system 100 includes: a processing module 103 , a communication module 104 and a storage module 105 .

[0146] The processing module 103 is used to control and manage the operation of the air conditioning system 100. The communication module 104 is used to support the communication between the air conditioning system 100 and other network entities. The storage module 105 is used to store the program code and data of the air conditioning system 100.

[0147] The processing module 103 may be a processor 1031. It may implement or execute the various exemplary logic blocks, modules, and circuits described in conjunction with the present disclosure. The processor 1031 may also be a combination of devices that implement computing functions, such as a combination of one or more microprocessors 1031, a combination of a digital signal processor (DSP) and a microprocessor, and so on. The communication module 104 may be a communication interface 1042. The storage module 105 may be a memory 1051.

[0148] When the processing module 103 is the processor 1031, the communication module 104 is the communication interface 1042, and the storage module 105 is the memory 1051, the air conditioning system 100 may be Figure 15 The device shown.

[0149] Figure 15 A schematic diagram of the composition of an air conditioning system 100 provided in an embodiment of the present invention is shown as follows: Figure 15 As shown, the air conditioning system 100 may include: at least one processor 1031 and a memory 1051 .

[0150] The following combination Figure 15 The various components of the air conditioning system 100 are described in detail:

[0151] The processor 1031 is the control center of the air conditioning system 100 and can be a single processor 1031 or a collective term for multiple processing elements. For example, the processor 1031 can be a central processing unit (CPU), an application-specific integrated circuit (ASIC), or one or more integrated circuits configured to implement embodiments of the present invention, such as one or more DSPs or one or more field programmable gate arrays (FPGAs).

[0152] In a specific implementation, as an embodiment, the processor 1031 may include one or more CPUs, such as Figure 15 0 and CPU1 are shown in FIG. Furthermore, as an embodiment, the air conditioning system 100 may include multiple processors 1031 , each of which may be a single-core processor (Single-CPU) or a multi-core processor (Multi-CPU). The processor 1031 herein may refer to one or more devices, circuits, and / or processing cores for processing data (e.g., computer program instructions).

[0153] The memory 1051 may be a read-only memory (ROM) or other type of static storage device that can store static information and instructions, a random access memory (RAM) or other type of dynamic storage device that can store information and instructions, or an electrically erasable programmable read-only memory (EEPROM), a compact disc (CD-ROM) or other optical disc storage, an optical disc storage (including a compact disc, laser disc, optical disc, digital versatile disc, Blu-ray disc, etc.), a magnetic disk storage medium or other magnetic storage device, or any other medium that can be used to carry or store desired program code in the form of instructions or data structures and can be accessed by a computer, but is not limited thereto. The memory 1051 may be independent and connected to the processor 1031 via the communication bus 1041. The memory 1051 may also be integrated with the processor 1031.

[0154] In a specific implementation, the memory 1051 is used to store the data of the present invention and execute the software programs of the present invention. The processor 1031 can execute the various functions of the air conditioning system 100 by running or executing the software programs stored in the memory 1051 and calling the data stored in the memory 1051.

[0155] The air conditioning system 100 may further include a communication interface 1042 and a communication bus 1041 .

[0156] The communication interface 1042 , which uses any transceiver or other device, is used to communicate with other devices or communication networks, such as a Radio Access Network (RAN) or a Wireless Local Area Network (WLAN). The communication interface 1042 may include a receiving unit to implement a receiving function and a sending unit to implement a sending function.

[0157] The communication bus 1041 can be an Industry Standard Architecture (ISA) bus, a Peripheral Component Interconnect (PCI) bus, or an Extended Industry Standard Architecture (EISA) bus. This bus can be divided into an address bus, a data bus, a control bus, etc. For ease of representation, Figure 15 Only one thick line is used in the diagram, but this does not mean that there is only one bus or one type of bus.

[0158] Through the description of the above implementation methods, technical personnel in the relevant field can clearly understand that for the convenience and simplicity of description, only the division of the above-mentioned functional modules is used as an example. In actual applications, the above-mentioned functions can be assigned to different functional modules as needed, that is, the internal structure of the device can be divided into different functional modules to complete all or part of the functions described above.

[0159] In the several embodiments provided by the present invention, it should be understood that the disclosed devices and methods can be implemented in other ways. For example, the device embodiments described above are merely illustrative. For example, the division of the modules or units is merely a logical function division. In actual implementation, there may be other division methods, such as multiple units or components can be combined or integrated into another device, or some features can be ignored or not executed. In addition, the mutual coupling or direct coupling or communication connection shown or discussed can be through some interfaces, indirect coupling or communication connection of devices or units, which can be electrical, mechanical or other forms.

[0160] The units described as separate components may or may not be physically separate, and the components shown as units may be one physical unit or multiple physical units, that is, they may be located in one place or distributed in multiple places. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

[0161] In addition, the functional units in the various embodiments of the present invention may be integrated into a single processing unit, each unit may exist physically separately, or two or more units may be integrated into a single unit. The aforementioned integrated units may be implemented in the form of hardware or software functional units.

[0162] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a readable storage medium. Based on this understanding, the technical solution of the embodiment of the present invention, or the part that contributes to the existing technology, or all or part of the technical solution can be embodied in the form of a software product, which is stored in a storage medium and includes several instructions for causing a device (which can be a single-chip microcomputer, chip, etc.) or a processor to execute all or part of the steps of the method described in each embodiment of the present invention. The aforementioned storage medium includes: various media that can store program code, such as a USB flash drive, a mobile hard disk, ROM, RAM, a magnetic disk, or an optical disk.

[0163] In the description of this specification, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

[0164] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any modifications or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be based on the scope of protection of the claims.

Claims

1. An air conditioning system, characterized in that: include: a compressor having a suction port and an exhaust port; A reversing assembly having a first valve port, a second valve port, a third valve port and a fourth valve port; The first valve port is connected to the exhaust port, and the fourth valve port is connected to the intake port; an indoor heat exchanger, wherein a first end of the indoor heat exchanger is connected to the second valve port; an outdoor heat exchanger assembly comprising a first portion and a second portion, wherein a first end of the first portion is connected to the third valve port, a first on-off valve is connected in series between the first end of the second portion and the third valve port, a first throttle valve is connected between the second end of the first portion and the second end of the indoor heat exchanger, and a second throttle valve is connected between the second end of the second portion and the second end of the indoor heat exchanger; a defrost branch, wherein a first end of the defrost branch is connected to the exhaust port, a second end of the defrost branch is connected to a pipeline between the first throttle valve and the second end of the first part, and a second on-off valve is connected in series to the defrost branch; A bypass branch, wherein the first end of the bypass branch is connected to the first end of the second part, the second end of the bypass branch is connected to the pipeline between the first throttle valve and the second end of the first part, and a third throttle valve is connected in series on the bypass branch.

2. The air conditioning system according to claim 1, characterized in that The first portion is located directly above the second portion; or, the first portion is located directly below the second portion.

3. The air conditioning system according to claim 1, characterized in that The second end of the bypass branch is connected to a pipeline between the second end of the defrost branch and the second end of the first portion.

4. The air conditioning system according to claim 1, characterized in that The reversing component is a four-way reversing valve.

5. The air conditioning system according to claim 1, characterized in that The first throttle valve, the second throttle valve and the third throttle valve are all electronic expansion valves.

6. The air conditioning system according to claim 1, characterized in that The first part and the second part are two independent heat exchangers, or the first part and the second part are two parts of the same heat exchanger.

7. The air conditioning system according to claim 1, characterized in that The first on-off valve is a two-way valve; and / or the second on-off valve is a solenoid valve.

8. The air conditioning system according to claim 1, characterized in that The first throttle valve and the second throttle valve are connected to the second end of the indoor heat exchanger through the same subcooler.

9. The air conditioning system according to claim 1, characterized in that It also includes a gas-liquid separator, which is arranged between the compressor and the reversing component. The gas-liquid separator has a liquid inlet and a gas outlet. The liquid inlet is connected to the fourth valve port, and the gas outlet is connected to the air intake.

10. The air conditioning system according to claim 1, wherein: It also includes an oil-gas separator, which has an inlet, a gas discharge port and an oil outlet. The inlet is connected to the exhaust port, the gas discharge port is connected to the first valve port, and the oil outlet is connected to the intake port.

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