Air supply control method for air conditioners

Abstract

This invention relates to the field of air conditioning technology, specifically to a method for controlling gas supply in an air conditioner. This application aims to solve the problems of high compressor cylinder temperature and poor stability. The air conditioner of this application has a gas supply port on the compressor cylinder. The air conditioner also includes a flow divider and a valve mechanism. The outdoor heat exchanger includes a first pipe section and a second pipe section. The outlet of the first pipe section is connected to a mixing inlet pipe, and the liquid outlet pipe is connected to the inlet of the second pipe section. The inlet of the valve mechanism is connected to a gas outlet pipe, and the outlet of the valve mechanism is connected to the gas supply port. The control method includes: acquiring the operating mode of the air conditioner; when the operating mode is cooling mode or dehumidification mode, acquiring the first discharge temperature of the compressor; based on the magnitude of the first discharge temperature and a first temperature threshold; selectively controlling the valve mechanism to open. This application utilizes the return of gaseous refrigerant in the outdoor heat exchanger to the compressor to cool the compressor, ensuring the operating stability of the compressor.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more specifically to a method for controlling the gas supply to an air conditioner. Background Technology

[0002] With advancements in science and technology and the worsening energy crisis, the home appliance industry is striving to reduce overall appliance costs and energy consumption. Taking air conditioners as an example, to achieve efficiency gains and cost reductions, for air conditioners of the same capacity, compressor displacement is decreasing, while the compressor's operating frequency and pressure ratio are correspondingly increasing. This inevitably leads to higher temperatures in the compressor's cylinder and motor. Higher temperatures in the cylinder and motor have a greater impact on the compressor's operational reliability, thus affecting the overall reliability of the air conditioner.

[0003] Accordingly, a new technical solution is needed in this field to solve the above problems. Summary of the Invention

[0004] To address at least one of the aforementioned problems in the prior art, namely, the high cylinder and motor temperatures and poor compressor stability resulting from the miniaturized design of existing air conditioners, this application provides a gas injection control method for an air conditioner. The air conditioner includes a compressor, an outdoor heat exchanger, a throttling element, and an indoor heat exchanger. A gas injection port is provided on the compressor cylinder. The air conditioner also includes a flow divider and a valve mechanism. The flow divider includes a housing and a mixing inlet pipe, a gas outlet pipe, and a liquid outlet pipe disposed on the housing. The outdoor heat exchanger includes a first pipe section and a second pipe section. The inlet of the first pipe section is connected to the compressor, and the outlet of the first pipe section is connected to the mixing inlet pipe. The liquid outlet pipe is connected to the inlet of the second pipe section, and the outlet of the second pipe section is connected to the inlet of the throttling element. The inlet of the valve mechanism is connected to the gas outlet pipe, and the outlet of the valve mechanism is connected to the gas injection port.

[0005] The gas replenishment control method includes:

[0006] Obtain the operating mode of the air conditioner;

[0007] When the operating mode is cooling mode or dehumidification mode, the first discharge temperature of the compressor is obtained;

[0008] Determine the magnitude of the first exhaust temperature and the first temperature threshold.

[0009] Based on the judgment result, the valve mechanism is selectively controlled to open.

[0010] In the preferred embodiment of the above-mentioned air supply control method for air conditioners, the step of "selectively controlling the valve mechanism to open based on the judgment result" further includes:

[0011] When the first exhaust temperature is greater than or equal to the first temperature threshold, the valve mechanism is controlled to open;

[0012] When the first exhaust temperature is less than the first temperature threshold, the valve mechanism is kept closed.

[0013] In the preferred embodiment of the above-mentioned air replenishment control method for air conditioners, after the step of "controlling the valve mechanism to open", the air replenishment control method further includes:

[0014] Obtain the second exhaust temperature of the compressor;

[0015] Determine the magnitude of the second exhaust temperature and the second temperature threshold.

[0016] Based on the judgment result, the valve mechanism is selectively controlled to close;

[0017] Wherein, the second temperature threshold is less than the first temperature threshold.

[0018] In the preferred embodiment of the above-mentioned air replenishment control method for air conditioners, the step of "selectively controlling the valve mechanism to close based on the judgment result" further includes:

[0019] When the second exhaust temperature is less than the second temperature threshold and the duration is greater than or equal to the preset duration threshold, the valve mechanism is controlled to close.

[0020] When the second exhaust temperature is greater than or equal to the second temperature threshold and / or the duration for which the second exhaust temperature is less than the second temperature threshold is less than the preset duration threshold, the valve mechanism is controlled to remain open.

[0021] In the preferred embodiment of the above-mentioned air conditioning unit gas replenishment control method, the mixing inlet pipe is located in the middle of the bottom surface of the outer casing, the gas outlet pipe and the liquid outlet pipe are both located on the top surface of the outer casing, and the liquid outlet pipe is located in the middle of the top surface. A separation pipe is provided inside the outer casing, and the two ends of the separation pipe are respectively connected to the mixing inlet pipe and the liquid outlet pipe. The separation pipe has micro-holes, and the separation pipe is connected to the gas outlet pipe through the micro-holes. The flow divider is configured to allow a portion of the gaseous refrigerant in the gas-liquid mixed refrigerant entering through the mixing inlet pipe to flow out through the gas outlet pipe, while the remaining gas-liquid mixed refrigerant flows out through the liquid outlet pipe.

[0022] In the preferred embodiment of the above-mentioned air replenishment control method for air conditioners, the diameters of the mixing inlet pipe and the liquid outlet pipe are both larger than the diameter of the separation pipe.

[0023] In a preferred embodiment of the above-mentioned air supply control method for air conditioners, the micropores are located at the middle of the separation tube along its length; and / or

[0024] Two micropores are provided, and the two micropores are arranged opposite each other along the radial direction of the separation tube; and / or

[0025] The diameter of the micropores is 0.3-0.5 mm.

[0026] In the preferred embodiment of the above-mentioned air replenishment control method for air conditioners, the outer casing is frustum-shaped.

[0027] In the preferred embodiment of the above-mentioned air supply control method for air conditioners, multiple gas outlet pipes are provided, and the multiple gas outlet pipes are evenly distributed circumferentially along a concentric circle with the outer circle of the top surface of the outer casing.

[0028] In a preferred embodiment of the above-mentioned air replenishment control method for an air conditioner, the radius of the outer circle of the top surface of the outer casing is larger than the radius of the outer circle of the bottom surface of the outer casing; and / or

[0029] The ratio of the radius of the concentric circles to the radius of the outer circle of the top surface of the outer shell is 0.5-0.75.

[0030] It should be noted that, in the preferred technical solution of this application, the air conditioner includes a compressor, an outdoor heat exchanger, a throttling element, and an indoor heat exchanger. The compressor cylinder is provided with a gas inlet. The air conditioner also includes a flow distribution device and a valve mechanism. The flow distribution device includes a housing and a mixing inlet pipe, a gas outlet pipe, and a liquid outlet pipe disposed on the housing. The outdoor heat exchanger includes a first pipe section and a second pipe section. The inlet of the first pipe section is connected to the compressor, the outlet of the first pipe section is connected to the mixing inlet pipe, the liquid outlet pipe is connected to the inlet of the second pipe section, the outlet of the second pipe section is connected to the inlet of the throttling element, the inlet of the valve mechanism is connected to the gas outlet pipe, and the outlet of the valve mechanism is connected to the gas inlet. The control method includes: acquiring the operating mode of the air conditioner; when the operating mode is cooling mode or dehumidification mode, acquiring the first discharge temperature of the compressor; determining the magnitude of the first discharge temperature and a first temperature threshold; and selectively controlling the valve mechanism to open based on the determination result.

[0031] The air conditioning unit gas replenishment control method disclosed in this application reduces the temperature of the compressor cylinder and motor during operation and improves the compressor's operational stability by installing a flow divider between the first and second pipe sections of the outdoor heat exchanger, with the gas outlet pipe of the flow divider connected to the compressor's gas replenishment port. Specifically, during the cooling process, the refrigerant passing through the first pipe section liquefies into a gas-liquid mixture. This mixture then enters the flow divider, where the liquid refrigerant continues to circulate, while the gaseous refrigerant returns to the compressor's gas replenishment port through the gas outlet pipe, cooling the compressor cylinder and preventing excessively high temperatures in the compressor cylinder and motor. By placing the flow divider between the first and second pipe sections of the outdoor heat exchanger, the refrigerant pressure allows for rapid separation and return of the gaseous refrigerant, improving the cooling effect on the compressor cylinder. A valve mechanism further enables automatic control of cylinder cooling, improving control accuracy.

[0032] In terms of control methods, by obtaining the first discharge temperature of the compressor in cooling or dehumidification mode, the temperature inside the compressor cylinder can be indirectly determined. When the temperature inside the compressor cylinder is too high, the valve mechanism is opened, and the gaseous refrigerant in the outdoor heat exchanger is returned to the compressor to cool it down, thus ensuring the stability of the compressor's operation.

[0033] Furthermore, by selectively closing the valve mechanism based on the second exhaust temperature, the compressor cylinder temperature can be kept within a reasonable range, preventing the exhaust temperature from dropping due to excessively low compressor cylinder temperature and thus affecting air conditioning performance.

[0034] Furthermore, the flow-dividing device is configured such that a portion of the gaseous refrigerant in the gas-liquid mixture entering through the mixing inlet pipe passes through micropores and flows out through the gas outlet pipe, while the remaining gas-liquid mixture flows out through the liquid outlet pipe. Thus, after the gaseous refrigerant becomes a medium-temperature, medium-pressure gas-liquid mixture in the first pipe section, it enters the mixing inlet pipe at high speed. A portion of the refrigerant flashes into gaseous form due to pressure drop and friction. This flashed gaseous refrigerant, resisted by the liquid refrigerant ahead, passes through the micropores and flows back through the gas outlet pipe to the compressor's gas inlet, cooling the compressor cylinder. The majority of the gas-liquid mixture continues to flow forward under the centrifugal force of the high-speed liquid flow, entering the second pipe section to continue heat exchange. Secondly, compared to existing gas-liquid separators, the flow-dividing device of this application can separate a portion of the gaseous refrigerant, reducing refrigerant pressure drop. Furthermore, this application features a cavity containing only one separation tube, with both ends connected to the mixing inlet and liquid outlet tubes, facilitating product miniaturization. The miniaturized distribution device can be directly integrated with an outdoor heat exchanger, such as by connecting it directly between two refrigerant pipes, without requiring a separate unit. The mixing inlet tube is positioned in the center of the bottom surface, and the liquid outlet tube in the center of the top surface, simplifying the manufacturing process and allowing the separation tube to be a straight pipe, minimizing pressure loss along the flow path.

[0035] Furthermore, by setting the diameters of both the mixing inlet pipe and the liquid outlet pipe to be larger than the diameter of the separator pipe, the flow velocity of the gas-liquid mixed refrigerant in the separator pipe can be increased, the pressure drop of the refrigerant can be reduced, and the gas-liquid separation effect can be guaranteed.

[0036] Furthermore, by placing the micropores in the middle of the separation tube along its length, a better gas-liquid separation effect can be obtained.

[0037] Furthermore, by setting up multiple gas outlet pipes, the separation amount of gaseous refrigerant can be guaranteed.

[0038] Furthermore, by making the outer shell truncated cone-shaped with the radius of the outer circle of the top surface being larger than the radius of the outer circle of the bottom surface, the installation space of the diversion device can be saved, making the installation method more flexible, and reducing pressure drop and refrigerant flow noise. Attached Figure Description

[0039] The air supply control method for the air conditioner of this application will now be described with reference to the accompanying drawings. In the drawings:

[0040] Figure 1 This is a system diagram of the air conditioner of this application;

[0041] Figure 2 This is a cross-sectional view of the diversion device of this application;

[0042] Figure 3 This is a diagram showing the refrigerant flow path of the diversion device in this application;

[0043] Figure 4 This is a top view of the diversion device of this application;

[0044] Figure 5 This is a top view of an alternative embodiment of the diversion device in this application;

[0045] Figure 6 A flowchart of the air supply control method for the air conditioner according to this application;

[0046] Figure 7 This is a logic diagram of one embodiment of the air supply control method for the air conditioner of this application.

[0047] List of reference numerals

[0048] 1. Compressor; 11. Gas inlet; 2. Outdoor heat exchanger; 21. First pipe section; 22. Second pipe section; 3. Throttling element; 4. Indoor heat exchanger; 5. Four-way valve; 6. Flow divider; 61. Outer shell; 62. Mixing inlet pipe; 63. Gas outlet pipe; 64. Liquid outlet pipe; 65. Separator pipe; 66. Micro-orifice; 7. Valve mechanism; 71. Valve mechanism inlet; 72. Valve mechanism outlet. Detailed Implementation

[0049] Preferred embodiments of this application are described below with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of this application and are not intended to limit the scope of protection of this application. For example, although this embodiment is described in conjunction with a wall-mounted air conditioner, this is not intended to limit the scope of protection of this application. Those skilled in the art can apply this application to other application scenarios without departing from the principles of this application. For example, this application can also be applied to cabinet air conditioners, recessed air conditioners, etc.

[0050] It should be noted that in the description of this application, terms such as "upper," "lower," "vertical," "inner," and "outer," indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. These are used merely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0051] Furthermore, it should be noted that, in the description of this application, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0052] First refer to Figure 1 and Figure 2 This paper describes the air conditioner described in this application. Among other things, Figure 1 This is a system diagram of the air conditioner in cooling mode according to this application; Figure 2 This is a cross-sectional view of the diversion device of this application.

[0053] like Figure 1 and Figure 2 As shown, to address the issues of high cylinder and motor temperatures and poor compressor stability caused by the miniaturized design of existing air conditioners, the air conditioner of this application includes a compressor 1, an outdoor heat exchanger 2, a throttling element 3, an indoor heat exchanger 4, a four-way valve 5, and a flow divider 6. The compressor 1 has a gas inlet 11 on its cylinder. The four-way valve 5 includes four ports: P, E, S, and C. The outdoor heat exchanger 2 includes a first pipe section 21 and a second pipe section 22. The flow divider 6 includes a housing 61 and a mixing inlet pipe 62, a gas outlet pipe 63, and a liquid outlet pipe 64 disposed on the housing 61.

[0054] With the connections complete, the exhaust port of compressor 1 is connected to the P port of four-way valve 5, and the suction port of compressor 1 is connected to the S port of four-way valve 5. The C port of four-way valve 5 is connected to the inlet of the first pipe section 21, the outlet of the first pipe section 21 is connected to the mixing inlet pipe 62 of the flow divider 6, the gas outlet pipe 63 is connected to the inlet 71 of valve mechanism 7, the outlet 72 of valve mechanism 7 is connected to the gas supply port 11 of compressor 1, the liquid outlet pipe 64 is connected to the inlet of the second pipe section 22, the outlet of the second pipe section 22 is connected to the inlet of throttling element 3, the throttling element 3 is connected to the inlet of indoor heat exchanger 4, and the outlet of indoor heat exchanger 4 is connected to the E port of four-way valve 5.

[0055] Under the above configuration, when the air conditioner operates in cooling mode, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 enters the first pipe section 21 of the outdoor heat exchanger 2 after passing through the P and C ports of the four-way valve 5. It undergoes heat exchange and liquefaction, becoming a medium-temperature, high-pressure saturated gas-liquid mixture. Subsequently, the gas-liquid mixture enters through the mixing inlet pipe 62, and then the gaseous refrigerant flows out through the gas outlet pipe 63 and back to the compressor 1's gas inlet 11. The liquid refrigerant continues to enter the second pipe section 22 for cooling and heat exchange, and finally flows out through the outlet of the second pipe section 22 into the throttling element 3 for throttling. After passing through the throttling element 3, the liquid refrigerant becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant. This low-temperature, low-pressure gas-liquid two-phase refrigerant then enters the indoor heat exchanger 4 through the inlet, where it exchanges heat with the indoor air to achieve evaporation, becoming a gaseous refrigerant. The gaseous refrigerant returns to the compressor 1 from the suction port of the compressor 1 after passing through the E and S ports of the four-way valve 5 from the outlet of the indoor heat exchanger 4.

[0056] By installing a flow divider 6 between the first pipe section 21 and the second pipe section 22 of the outdoor heat exchanger 2, and connecting the gas outlet pipe 63 of the flow divider 6 to the gas inlet 11 of the compressor 1, the temperature of the compressor cylinder and motor during operation can be reduced, thus improving the operational stability of the compressor 1. Specifically, during the refrigeration process, the refrigerant passing through the first pipe section 21 liquefies into a gas-liquid mixture. This mixture then enters the flow divider 6, where the liquid refrigerant continues to circulate, while the gaseous refrigerant flows back to the gas inlet 11 of the compressor 1 through the gas outlet pipe 63, cooling the compressor cylinder and preventing excessively high temperatures in the compressor cylinder and motor. By placing the flow divider 6 between the first pipe section 21 and the second pipe section 22 of the outdoor heat exchanger 2, the refrigerant pressure can be used to achieve rapid separation and reflux of the gaseous refrigerant, improving the cooling effect of the compressor cylinder.

[0057] The following reference Figures 1 to 4 This paper describes a preferred embodiment of the air conditioner according to the present application. Figure 3 This is a diagram showing the refrigerant flow path of the diversion device in this application; Figure 4 This is a top view of the diversion device of this application.

[0058] like Figure 1 and Figure 2 As shown, in a preferred embodiment, the air conditioner is a wall-mounted air conditioner, which includes an indoor unit and an outdoor unit. The outdoor unit is equipped with a compressor 1, a four-way valve 5, a throttling element 3, an outdoor heat exchanger 2, and a flow divider 6, etc., while the indoor unit is equipped with an indoor heat exchanger 4, etc. A gas injection port 11 is provided in the middle of the compressor 1 cylinder, through which gaseous refrigerant enters the compressor 1 to achieve medium-pressure gas injection.

[0059] The outdoor heat exchanger 2 includes a first pipe section 21 and a second pipe section 22, with the first pipe section 21 located above the second pipe section 22. The first pipe section 21 is divided into two flow paths, with its inlet located in the middle. After entering through the inlet of the first pipe section 21, the refrigerant flows along both the upper and lower flow paths, then merges and enters the mixing inlet pipe 62 of the flow divider 6. The inlet of the second pipe section 22 is located at the upper part, and its outlet is located at the lower part. The inlet of the second pipe section 22 is connected to the liquid outlet pipe 64 of the flow divider 6, and its outlet is connected to the inlet of the throttling element 3.

[0060] The outdoor unit of the air conditioner also includes a valve mechanism 7. The gas outlet pipe 63 of the distribution device 6 is connected to the inlet 71 of the valve mechanism 7, and the outlet 72 of the valve mechanism 7 is connected to the gas supply port 11 of the compressor 1. The valve mechanism 7 is configured such that when open, the inlet 71 of the valve mechanism 7 is connected to the outlet 72 of the valve mechanism 7, and when closed, the inlet 71 of the valve mechanism 7 is disconnected from the outlet 72 of the valve mechanism 7. The valve mechanism 7 can be a reversing valve, a solenoid valve, etc.

[0061] When the inlet 71 of the valve mechanism 7 is connected to the outlet 72 of the valve mechanism 7, the gaseous refrigerant separated by the diverter 6 can flow back to the air supply port 11 of the compressor 1 to cool the cylinder of the compressor 1.

[0062] For example, in cooling mode, the cylinder of compressor 1 is prone to high temperatures. At this time, by connecting the inlet 71 and outlet 72 of the control valve mechanism 7, gaseous refrigerant can be returned to the gas inlet 11 of compressor 1 to cool the cylinder. Through careful research, calculation, and analysis, the inventors have determined that the temperature of the gaseous refrigerant entering the gas inlet 11 of compressor 1 can be controlled between 45-55°C. During cooling operation, the cylinder temperature is typically between 80-150°C. The added gaseous refrigerant effectively reduces the cylinder temperature, maintaining it within a reasonable temperature range and ensuring the stability and reliability of compressor 1.

[0063] See Figure 2 and Figure 4In a preferred embodiment, the diversion device 6 includes a housing 61, which is an inverted frustum shape, meaning the radius of the outer circle of the top surface of the housing 61 is larger than the radius of the outer circle of the bottom surface. A cavity is formed inside the housing 61, and a separation pipe 65 is disposed within the cavity. A mixing inlet pipe 62 is disposed on the bottom surface of the housing 61, and a gas outlet pipe 63 and a liquid outlet pipe 64 are disposed on the top surface of the housing 61. The two ends of the separation pipe 65 are respectively connected to the mixing inlet pipe 62 and the liquid outlet pipe 64, and micropores 66 are formed on the separation pipe 65. The diversion device 6 is configured to allow a portion of the gaseous refrigerant in the gas-liquid mixture entering through the mixing inlet pipe 62 to flow out through the gas outlet pipe 63, while the remaining gas-liquid mixture flows out through the liquid outlet pipe 64. Preferably, when installed between the first pipe section 21 and the second pipe section 22 of the condenser, the diversion device 6 is installed upright.

[0064] Preferably, see Figure 2 The mixing inlet pipe 62 is located in the middle of the bottom surface, and the liquid outlet pipe 64 is located in the middle of the top surface. The separation pipe 65 is a straight pipe, and its two ends are directly connected to the mixing inlet pipe 62 and the liquid outlet pipe 64, respectively. Regarding the pipe diameter, the diameter of the mixing inlet pipe 62 (i.e.,...) Figure 2 a) and the diameter of the liquid outlet pipe 64 (i.e. Figure 2 In section b), all diameters are greater than those of the separator 65 (i.e., ...). Figure 2 (c) In one specific embodiment, the length of the separation tube 65 can be any value between 35-38 mm, the diameter of the mixing inlet tube 62 can be any value between 6.35-8.5 mm, the diameter of the liquid outlet tube 64 can be any value between 4.5-6.35 mm, and the diameter of the separation tube 65 can be any value between 4.0-4.5 mm.

[0065] See Figure 2 and Figure 4 Multiple gas outlet pipes 63 are provided. In this application, two gas outlet pipes 63 are provided. The two gas outlet pipes 63 are evenly distributed circumferentially along concentric circles with the outer circle of the top surface of the outer shell 61, so that the center of the cross-section of the two gas outlet pipes 63 and the center of the cross-section of the liquid outlet pipe 64 are connected by a straight line. The diameter of the two gas outlet pipes 63 (i.e., Figure 2 The values ​​of 'd' in the diagram are equal, and both are equal to the diameter of the liquid outlet pipe 64. The radii of the concentric circles (i.e.,...) Figure 4 The radius of the outer circle of the top surface of the outer shell 61 (i.e., r) is the radius of the outer circle of the top surface of the outer shell 61. Figure 4 The ratio of R to R is 0.5-0.75. In one specific embodiment, the radius of the outer circle of the top surface of the outer shell 61 can be any value between 12-15 mm, and the radius of the concentric circles can be any value between 6-9 mm.

[0066] See back Figure 2Two micro-holes 66 are provided, arranged radially opposite to each other along the separation tube 65, and located at the middle of the separation tube 65 along its length. In this application, the diameter of the micro-holes 66 is 0.3-0.5 mm, and the line connecting the axes of the two micro-holes 66 is parallel to the line connecting the centers of the cross-sections of the two gas outlet tubes 63 and lies in the same vertical plane. In other words, the opening direction of the two micro-holes 66 is exactly towards the axial direction of the two gas outlet tubes 63.

[0067] See Figure 3 In the above configuration, when the gas-liquid mixed refrigerant enters the separation pipe 65 through the mixing inlet pipe 62, most of the gas-liquid mixed refrigerant continues to flow forward under the centrifugal force of the high-speed liquid flow, and eventually flows out through the liquid outlet pipe 64. Meanwhile, some refrigerant flashes into gaseous refrigerant due to pressure drop and friction. This gaseous refrigerant, resisted by the liquid refrigerant ahead, passes through the micropores 66 and flows out through the gas outlet pipe 63, thus achieving effective separation of some of the gaseous refrigerant.

[0068] The flow divider 6 of this application is configured such that a portion of the gaseous refrigerant in the gas-liquid mixture entering through the mixing inlet pipe 62 passes through the micropores 66 and flows out through the gas outlet pipe 63, while the remaining gas-liquid mixture flows out through the liquid outlet pipe 64. Thus, after the gaseous refrigerant becomes a medium-temperature, medium-pressure gas-liquid mixture after passing through the first pipe section 21, the gas-liquid mixture refrigerant enters the mixing inlet pipe 62 at high speed. Part of the refrigerant flashes into gaseous refrigerant due to pressure drop and friction. This flashed gaseous refrigerant, resisted by the liquid refrigerant ahead, passes through the micropores 66 and flows back through the gas outlet pipe 63 to the compressor 1's air inlet 11, cooling the compressor 1 cylinder. The majority of the gas-liquid mixture refrigerant continues to flow forward under the centrifugal force of the high-speed liquid flow, entering the second pipe section 22 to continue participating in heat exchange. Furthermore, compared to existing gas-liquid separators, the flow divider 6 of this application can achieve partial separation of the gaseous refrigerant, reducing refrigerant pressure drop. Furthermore, as can be seen from the aforementioned dimensional parameters, the cavity of this application contains only one separation tube 65, and both ends of the separation tube 65 are connected to the mixing inlet tube 62 and the liquid outlet tube 64, making it easier to achieve product miniaturization. Moreover, the miniaturized flow divider 6 can be directly used in conjunction with the outdoor heat exchanger 2, such as by directly connecting it between two refrigerant pipes, without needing to occupy space as a separate device. The mixing inlet tube 62 is located in the middle of the bottom surface, and the liquid outlet tube 64 is located in the middle of the top surface, simplifying the product manufacturing process and allowing the separation tube 65 to be a straight tube, minimizing pressure loss along the pipe. By setting the diameters of both the mixing inlet tube 62 and the liquid outlet tube 64 to be larger than the diameter of the separation tube 65, the flow velocity of the gas-liquid mixed refrigerant in the separation tube 65 can be increased, reducing the refrigerant pressure drop and ensuring gas-liquid separation effect. By placing the micropores 66 in the middle of the separation tube 65 along its length, a better gas-liquid separation effect can be obtained. By setting multiple gas outlet tubes 63, the separation volume of gaseous refrigerant can be guaranteed. By using a frustum-shaped outer casing 61 with a larger radius on the top outer circle than on the bottom outer circle, space can be saved for the distribution device 6, allowing for more flexible installation and reducing pressure drop and refrigerant flow noise. The valve mechanism 7 enables automatic control of cylinder cooling, improving control precision.

[0069] It should be noted that the above preferred embodiments are merely illustrative of the principles of this application and are not intended to limit the scope of protection of this application. Without departing from the principles of this application, those skilled in the art can adjust the above settings to make this application applicable to more specific application scenarios.

[0070] For example, in an alternative embodiment, although the air conditioner of this application is described in conjunction with a four-way valve 5, it is clear that the diversion device 6 of this application can also be applied to a cooling-only air conditioner or a heating-only air conditioner.

[0071] For example, in another alternative embodiment, although in the diversion device 6 of this application, the mixing inlet pipe 62 is located in the middle of the bottom surface and there is only one of it, and the liquid outlet pipe 64 is located in the middle of the top surface and there is also only one of it, and the separation pipe 65 is a straight pipe with the diameters of both the mixing inlet pipe 62 and the liquid outlet pipe 64 being larger than the diameter of the separation pipe 65, this is not intended to limit the scope of protection of this application. In other embodiments, those skilled in the art can change the above-mentioned arrangement according to the specific application scenario. For example, the positions of the mixing inlet pipe 62 and the liquid outlet pipe 64 can be adjusted, and their number can also be adjusted. The separation pipe 65 can be set as a non-straight pipe, and its diameter can be greater than or equal to the diameters of the mixing inlet pipe 62 and the liquid outlet pipe 64, etc.

[0072] For example, in another alternative embodiment, the number of gas outlet pipes 63 is not fixed, and those skilled in the art can adjust their number based on design requirements. For example, with Figure 5 As shown in the example, the gas outlet pipe 63 can also be set to three, with the three gas outlet pipes 63 evenly distributed on the concentric circles of the outer circle of the top surface. Of course, the gas outlet pipe 63 can also be set to one, four or more.

[0073] For example, in another alternative embodiment, the arrangement of two micropores 66 located in the middle of the separation tube 65 along its length is not the only option; those skilled in the art can adjust it as needed. For instance, the number of micropores 66 can be adjusted based on the number of gas outlet tubes 63, and their placement can also be moved up or down.

[0074] For example, in another alternative embodiment, although the housing 61 is described as an inverted frustum shape, this is not the only embodiment. The shape of the housing 61 can also be cylindrical, rectangular, etc.

[0075] Of course, the alternative implementation methods described above, as well as the alternative implementation methods and preferred implementation methods, can be used in combination to create new implementation methods that are suitable for more specific application scenarios.

[0076] The following is combined with Figure 1 The working process of the air conditioner described in this application will be introduced.

[0077] See Figure 1When the air conditioner operates in cooling mode, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 1 enters the first pipe section 21 of the outdoor heat exchanger 2 through the P and C interfaces of the four-way valve 5, where it is split into two streams for heat exchange and liquefaction, becoming a medium-temperature, high-pressure saturated gas-liquid mixture. Subsequently, the two streams of liquefied gas-liquid mixture merge and enter the separation pipe 65 from the mixing inlet pipe 62. In the separation pipe 65, the liquid refrigerant, under the influence of centrifugal force, carries some of the gaseous refrigerant directly through the liquid outlet pipe 64 to the second pipe section 22. A portion of the gaseous refrigerant flashes out and passes through the micropores 66, flowing out through the two gas outlet pipes 63. The gaseous refrigerant flowing from the two gas outlet pipes 63 merges and enters the valve mechanism 7 through the inlet 71, then flows back to the compressor 1's gas inlet 11 from the outlet 72, cooling the compressor 1's cylinder. The gas-liquid mixture of refrigerant, containing a small amount of gaseous refrigerant, enters the second pipe section 22 and liquefies. It then flows out from the outlet of the second pipe section 22 and enters the throttling element 3 for throttling. After passing through the throttling element 3, the liquid refrigerant becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant. This low-temperature, low-pressure gas-liquid two-phase refrigerant enters the indoor heat exchanger 4 through the inlet, where it exchanges heat with the indoor air and evaporates, becoming a low-temperature, low-pressure gaseous refrigerant. The gaseous refrigerant then flows from the outlet of the indoor heat exchanger 4 through the E and S ports of the four-way valve 5 and returns to the compressor 1 from the suction port, completing one cycle.

[0078] The following reference Figure 6 This paper introduces the air supply control method for the air conditioner according to this application. Figure 6 This is a flowchart of the air supply control method for the air conditioner of this application.

[0079] like Figure 6 As shown, corresponding to the aforementioned air conditioner, this application also provides an air supply control method for an air conditioner, comprising:

[0080] S101. Obtain the operating mode of the air conditioner; for example, the operating mode may include cooling mode, heating mode, dehumidification mode and air supply mode, etc. After the user turns on the air conditioner, determine the operating mode of the air conditioner based on the mode selected by the user.

[0081] S103. When the operating mode is cooling mode or dehumidification mode, obtain the first discharge temperature of the compressor. For example, if the operating mode is cooling mode or dehumidification mode, the first discharge temperature of the compressor is obtained through a temperature sensor installed on the pipeline at the compressor discharge port. Of course, the first discharge temperature can also be obtained through other methods, such as indirectly calculating the discharge temperature through the pressure at the discharge port or the internal temperature of the compressor.

[0082] S105. Determine the magnitude of the first exhaust temperature and the first temperature threshold. For example, the first temperature threshold is preset by the factory, and the magnitude of the two is calculated by calculating the difference or ratio between the first exhaust temperature and the first temperature threshold.

[0083] S107. Based on the judgment result, selectively control the valve mechanism to open; for example, when the first exhaust temperature is greater than or equal to the first temperature threshold, control the valve mechanism to open; when the first exhaust temperature is less than the first temperature threshold, control the valve mechanism to remain closed.

[0084] By obtaining the first discharge temperature of the compressor in cooling or dehumidification mode, the temperature inside the compressor cylinder can be indirectly determined. When the temperature inside the compressor cylinder is too high, the valve mechanism is opened, and the gaseous refrigerant in the outdoor heat exchanger is returned to the compressor to cool it down, thus ensuring the stability of the compressor's operation.

[0085] The preferred embodiments of this application are described below.

[0086] In a preferred embodiment, S107 further includes: opening the control valve mechanism when the first exhaust temperature is greater than or equal to the first temperature threshold; and keeping the control valve mechanism closed when the first exhaust temperature is less than the first temperature threshold.

[0087] For example, the first temperature threshold can be any value between 80℃ and 90℃. When the first discharge temperature is greater than or equal to the first temperature threshold, it indicates that the compressor cylinder temperature is too high, which will have a certain impact on the compressor's performance and operational stability. At this time, the control valve mechanism opens, using the gaseous refrigerant in the outdoor heat exchanger to flow back to the compressor's gas inlet to cool the compressor cylinder. Conversely, if the first discharge temperature is less than the first temperature threshold, it indicates that the compressor cylinder temperature is within the normal range, and no action is required; the valve mechanism should remain closed.

[0088] In a preferred embodiment, after the control valve mechanism is opened, the control method further includes: acquiring a second discharge temperature of the compressor; determining the magnitude of the second discharge temperature and a second temperature threshold; and selectively controlling the valve mechanism to close based on the determination result; wherein the second temperature threshold is less than a first temperature threshold. Specifically, the control valve mechanism closes when the second discharge temperature is less than the second temperature threshold and the duration is greater than or equal to a preset duration threshold; and the control valve mechanism remains open when the second discharge temperature is greater than or equal to the second temperature threshold, and / or the duration of the second discharge temperature being less than the second temperature threshold is less than the preset duration threshold.

[0089] For example, after the control valve mechanism opens, a portion of the gaseous refrigerant in the outdoor heat exchanger enters the compressor through the gas inlet to cool and replenish the compressor cylinder. Since the compressor cylinder temperature exists within a suitable range, temperatures above or below this range are detrimental to compressor performance. Therefore, even after opening the valve mechanism, real-time monitoring of the cylinder temperature is still necessary. At this time, the second discharge temperature of the compressor is again obtained through a temperature sensor, and its relationship with a second temperature threshold is compared to determine whether the compressor is operating within a reasonable temperature range. The second temperature threshold can be any value between 60-70℃, and the preset duration threshold can be any value between 5s-20s. When the second discharge temperature is lower than the second temperature threshold and its duration is greater than or equal to the preset duration threshold, it indicates that the compressor cylinder temperature is too low, and the control valve mechanism closes. Conversely, if the second discharge temperature is greater than or equal to the second temperature threshold, and / or the duration of the second discharge temperature being lower than the second temperature threshold is less than the preset duration threshold, the compressor cylinder temperature is determined to be within the normal temperature range, and no action is required; the valve mechanism remains open.

[0090] By selectively closing the valve mechanism based on the second exhaust temperature, the compressor cylinder temperature can be kept within a reasonable range, preventing a drop in exhaust temperature due to excessively low compressor cylinder temperature, which would negatively impact air conditioning performance. Increasing the duration of the judgment process can improve accuracy and reduce false alarms.

[0091] The following reference Figure 7 This paper describes one possible control process for this application. Figure 7 This is a logic diagram of one embodiment of the air supply control method for the air conditioner of this application.

[0092] like Figure 7 As shown, in one possible control process:

[0093] S201, Obtain the operating mode of the air conditioner.

[0094] S203: Determine if the operating mode is cooling or dehumidification. If yes, proceed to S205; otherwise, terminate the program.

[0095] S205, obtain the first discharge temperature Tp1 of the compressor.

[0096] S207, determine if Tp1≥T1 is true. If true, proceed to S209; otherwise, proceed to S215. T1 is the first preset temperature.

[0097] S209, the control valve mechanism is open.

[0098] S211, obtain the second exhaust temperature Tp2 of the compressor.

[0099] S213, determine whether Tp2 < T2 and t ≥ Δt are both true. If true, proceed to S215; otherwise, if false, return to continue executing S209. Here, T2 is the second preset temperature, and Δt is the preset time threshold.

[0100] S215, control valve mechanism closed.

[0101] Those skilled in the art will understand that although some embodiments described herein include certain features included in other embodiments but not others, combinations of features from different embodiments are intended to be within the scope of this application and form different embodiments. For example, any of the claimed embodiments in the claims of this application can be used in any combination.

[0102] It should also be noted that although the detailed steps of the method of this application have been described in detail above, those skilled in the art can combine, split and rearrange the above steps without departing from the basic principles of this application. Such modified technical solutions do not change the basic concept of this application and therefore also fall within the protection scope of this application.

[0103] The technical solutions of this application have been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of this application is obviously not limited to these specific embodiments. Without departing from the principles of this application, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will all fall within the scope of protection of this application.

Claims

1. A method for controlling gas supply in an air conditioner, the air conditioner comprising a compressor, an outdoor heat exchanger, a throttling element, and an indoor heat exchanger, characterized in that, The cylinder of the compressor is provided with a supplementary air inlet, the air conditioner further comprises a flow splitting device and a valve mechanism, the flow splitting device comprises a shell and a mixed inlet pipe, a gas outlet pipe and a liquid outlet pipe arranged in the shell, the outdoor heat exchanger comprises a first pipe section and a second pipe section, the inlet of the first pipe section is communicated with the compressor, the outlet of the first pipe section is communicated with the mixed inlet pipe, the liquid outlet pipe is communicated with the inlet of the second pipe section, the outlet of the second pipe section is communicated with the inlet of the throttling element, the inlet of the valve mechanism is communicated with the gas outlet pipe, and the outlet of the valve mechanism is communicated with the supplementary air inlet, The mixed inlet pipe is arranged in the middle of the bottom surface of the shell, the gas outlet pipe and the liquid outlet pipe are arranged on the top surface of the shell, and the liquid outlet pipe is arranged in the middle of the top surface, a separation pipe is arranged in the shell, two ends of the separation pipe are communicated with the mixed inlet pipe and the liquid outlet pipe respectively, a plurality of micropores are arranged on the separation pipe, the separation pipe is communicated with the gas outlet pipe through the micropores, the flow splitting device is arranged to enable part of the gaseous refrigerant in the gas-liquid mixed refrigerant entering the mixed inlet pipe to flow out of the gas outlet pipe, and the remaining gas-liquid mixed refrigerant flows out of the liquid outlet pipe, the pipe diameter of the mixed inlet pipe and the pipe diameter of the liquid outlet pipe are both greater than the pipe diameter of the separation pipe, the shell is in the shape of a circular truncated cone, a plurality of gas outlet pipes are arranged, and the plurality of gas outlet pipes are uniformly distributed along the circumferences of concentric circles of the top surface of the shell, The supplementary air control method comprises the following steps: acquiring the working mode of the air conditioner; when the working mode is a refrigeration mode or a dehumidification mode, acquiring the first discharge temperature of the compressor; determining the size of the first discharge temperature and a first temperature threshold value; based on the determination result, selectively controlling the valve mechanism to open.

2. The air supply control method of claim 1, wherein, The step of "based on the determination result, selectively controlling the valve mechanism to open" further comprises the following steps: when the first discharge temperature is greater than or equal to the first temperature threshold value, controlling the valve mechanism to open; when the first discharge temperature is less than the first temperature threshold value, controlling the valve mechanism to remain closed.

3. The air supplement control method of claim 2, wherein, After the step of "controlling the valve mechanism to open", the supplementary air control method further comprises the following steps: acquiring the second discharge temperature of the compressor; determining the size of the second discharge temperature and a second temperature threshold value; based on the determination result, selectively controlling the valve mechanism to close; wherein the second temperature threshold value is less than the first temperature threshold value.

4. The air supply control method of claim 3, wherein, The step of "based on the determination result, selectively controlling the valve mechanism to close" further comprises the following steps: when the second discharge temperature is less than the second temperature threshold value and the duration is greater than or equal to a preset duration threshold value, controlling the valve mechanism to close; when the second discharge temperature is greater than or equal to the second temperature threshold value and / or the duration of the second discharge temperature being less than the second temperature threshold value is less than the preset duration threshold value, controlling the valve mechanism to remain open.

5. The method of claim 1, wherein the air supply control method is applied to an air conditioner. The micropores are arranged in the middle of the separation pipe in the length direction; and / or The micropores are arranged in the middle of the separation pipe in the length direction; and / or The micropores are arranged in the middle of the separation pipe in the length direction; and / or The micro-holes have a diameter of 0.3-0.5 mm.

6. The air supply control method of claim 1, wherein, The radius of the top surface of the housing is greater than the radius of the bottom surface of the housing; and / or The ratio of the radius of the concentric circle to the radius of the top surface of the housing is 0.5-0.75.

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