Air conditioner

Abstract

The embodiment of the utility model provides an air conditioner, and relates to the technical field of air conditioners, the air conditioner comprises a compressor, an outdoor heat exchanger, a liquid storage device and an indoor heat exchanger; a partition plate is arranged in the liquid storage device, an inner cavity of the liquid storage device is divided into a first chamber and a second chamber by the partition plate, and the partition plate is movably arranged so as to change the volume of the first chamber and the volume of the second chamber; the compressor, the outdoor heat exchanger, the first chamber and the indoor heat exchanger are sequentially communicated to form a refrigerant circulating flow path; the second cavity is further communicated with an exhaust port of the compressor so that the volume of the second cavity can be adjusted through exhaust of the compressor. Correspondingly, in the scheme of the embodiment, the storage amount of the refrigerant in the liquid storage device can be adjusted through the exhaust pressure of the compressor.

Description

Technical Field

[0001] This application relates to the technical field of air conditioners, specifically to an air conditioner. Background Technology

[0002] Dual-purpose (cooling and heating) air conditioners now dominate the residential air conditioning market. With the industry's energy efficiency levels improving year by year, high energy efficiency remains one of the core selling points of air conditioners. Therefore, high-efficiency dual-purpose air conditioners are not only a window for manufacturers to showcase their technological strength, but also a key factor in enhancing product market competitiveness. The refrigerant charge is a factor affecting air conditioner energy efficiency, influenced by factors such as operating conditions and system configuration. The optimal refrigerant charge required for dual-purpose air conditioners to achieve optimal performance in cooling and heating modes differs. Generally, the optimal refrigerant charge for heating mode is 5% to 30% higher than that for cooling mode. However, the refrigerant charge of existing air conditioning products cannot be adjusted according to changes in operating conditions. Therefore, the refrigerant charge is often not at the optimal point for system performance, resulting in suboptimal air conditioner energy efficiency. Utility Model Content

[0003] This application provides an air conditioner that can automatically adjust the amount of refrigerant used for circulation in different modes.

[0004] This application provides an air conditioner, including a compressor, an outdoor heat exchanger, a liquid receiver, and an indoor heat exchanger;

[0005] The liquid reservoir is provided with a partition, which divides the inner cavity of the liquid reservoir into a first chamber and a second chamber, and the partition is movable to change the volume of the first chamber and the second chamber;

[0006] The compressor, the outdoor heat exchanger, the first chamber, and the indoor heat exchanger are sequentially connected to form a refrigerant circulation path;

[0007] The second chamber is also connected to the exhaust port of the compressor so that the volume of the second chamber can be adjusted by the exhaust of the compressor.

[0008] In some embodiments, the air conditioner further includes a first control valve;

[0009] The first control valve is connected to the indoor heat exchanger, the outdoor heat exchanger, the exhaust port of the compressor, and the intake port of the compressor, respectively.

[0010] In some embodiments, the exhaust port of the compressor is connected to the second chamber via a capillary tube.

[0011] In some embodiments, the reservoir has a third interface and a fourth interface communicating with the second chamber, wherein the third interface is communicating with the exhaust port of the compressor;

[0012] The air conditioner also includes a second control valve, which is connected to the indoor heat exchanger, the outdoor heat exchanger, the fourth interface, and the air intake of the compressor.

[0013] In some embodiments, the first chamber and / or the second chamber are provided with elastic members;

[0014] One end of the elastic element is connected to the partition to provide resistance to the movement of the partition when the partition increases the volume of the second chamber.

[0015] In some embodiments, the air conditioner has a heating mode and a cooling mode;

[0016] When the air conditioner is in heating mode, the volume of the first chamber is a, and when the air conditioner is in cooling mode, the volume of the first chamber is b, where a < b.

[0017] In some embodiments, the reservoir further has a first interface and a second interface communicating with the first chamber;

[0018] The first interface is connected to the outdoor heat exchanger, and the second interface is connected to the indoor heat exchanger.

[0019] In some embodiments, a throttling component is further provided in the refrigerant circulation path, the throttling component being disposed between the second interface of the liquid receiver and the indoor heat exchanger.

[0020] In some embodiments, the throttling assembly includes a first filter, a throttler, and a second filter arranged sequentially, wherein the first filter is connected to the second interface, and the second filter is connected to the indoor heat exchanger.

[0021] In some embodiments, the first interface and the second interface are arranged opposite each other in the vertical direction, and the first interface is located below the second interface.

[0022] In the embodiments of this application, the compressor, the outdoor heat exchanger, the first chamber, and the indoor heat exchanger are sequentially connected to form a refrigerant circulation path. The second chamber is also connected to the exhaust port of the compressor, meaning the pressure in the second chamber can be considered similar to the pressure at the compressor's exhaust port. In cooling mode, the pressure in the first chamber can be approximated as being approximately the same as the refrigerant outlet pressure of the outdoor heat exchanger. Due to the flow resistance encountered by the refrigerant in the heat exchanger during condensation, the condensation outlet pressure will be slightly lower than the exhaust pressure. Therefore, at the beginning of the cooling mode, the pressure in the first chamber will be less than the pressure in the second chamber, releasing a small portion of the refrigerant. Refrigerant enters the refrigeration cycle. In heating mode, the pressure in the first chamber can be approximated as equal to the pressure at the refrigerant inlet of the indoor heat exchanger. Since the refrigerant inlet pressure of the indoor heat exchanger is much lower than the discharge pressure of the compressor, the pressure in the first chamber is much lower than the pressure in the second chamber at the beginning of heating mode. Under the pressure difference, the baffle increases the volume of the second chamber and decreases the volume of the first chamber, thereby releasing the refrigerant stored in the first chamber into the heating cycle to a great extent. This ensures that there is more refrigerant in the circulation path in heating mode than in the circulation path in cooling mode, thus improving the energy efficiency of the air conditioner. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Figure 1 This is a flow path diagram of the refrigerant circulation path in cooling mode provided in some embodiments of this application;

[0025] Figure 2 This is a flow path diagram of the refrigerant circulation path in heating mode provided in some embodiments of this application;

[0026] Figure 3 This is a flow diagram of the first embodiment of the air conditioner of this application in cooling mode;

[0027] Figure 4 This is a flow diagram of the first embodiment of the air conditioner of this application in heating mode;

[0028] Figure 5 yes Figure 3 A schematic diagram of the internal structure of the liquid receiver when the compressor is off;

[0029] Figure 6 yes Figure 3 A schematic diagram of the internal structure of the liquid receiver in low-load cooling mode;

[0030] Figure 7 yes Figure 3 A schematic diagram of the internal structure of the liquid receiver in high-load cooling mode;

[0031] Figure 8 yes Figure 3 A schematic diagram of the internal structure of the liquid reservoir in heating mode;

[0032] Figure 9 This is a flow diagram of the second embodiment of the air conditioner of this application in cooling mode;

[0033] Figure 10 This is a flow diagram of the second embodiment of the air conditioner of this application in heating mode;

[0034] Figure 11 yes Figure 9 A schematic diagram of the internal structure of the liquid reservoir;

[0035] Figure 12 This application provides a schematic diagram of the structure of the first chamber of the reservoir in some embodiments;

[0036] Figure 13 This is a schematic diagram of the structure of the first chamber of the reservoir in some other embodiments provided in this application.

[0037] Explanation of key component symbols:

[0038] label name label name 100 air conditioner 10 compressor 20 Outdoor heat exchanger 30 reservoir 31 First Interface 32 Second interface 33 Third interface 34 Fourth interface 40 Indoor heat exchanger 50 Throttling components 51 First filter 52 Throttling 53 Second filter 60 capillary 70 First control valve 80 Second control valve 35 First chamber 36 Second chamber 37 elastic element 38 partition 311 Upper connecting section 312 Liquid storage section 313 lower connecting section Detailed Implementation

[0039] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0040] In the description of this application, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, are used only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of 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 or implicitly specifying the number of indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of the stated features. In the description of this application, "a plurality of" means two or more, unless otherwise explicitly specified.

[0041] "A and / or B" includes the following three combinations: A only, B only, and a combination of A and B.

[0042] The use of "applies to" or "configured to" in this application implies open and inclusive language, which does not exclude the applicability to or configuration to devices performing additional tasks or steps. Additionally, the use of "based on" implies openness and inclusivity, because processes, steps, calculations, or other actions "based on" one or more of the stated conditions or values ​​may in practice be based on additional conditions or values ​​beyond those stated.

[0043] In this application, the term "exemplary" is used to mean "used as an example, illustration, or description." Any embodiment described as "exemplary" in this application is not necessarily to be construed as being more preferred or advantageous than other embodiments. The following description is provided to enable any person skilled in the art to make and use this application. Details are set forth in the following description for purposes of explanation. It should be understood that those skilled in the art will recognize that this application can be made without using these specific details. In other instances, well-known structures and processes are not described in detail to avoid obscuring the description of this application with unnecessary detail. Therefore, this application is not intended to be limited to the embodiments shown, but is consistent with the broadest scope of the principles and features disclosed in this application.

[0044] Dual-purpose (cooling and heating) air conditioners now dominate the residential air conditioning market. With the industry's energy efficiency levels improving year by year, high energy efficiency remains one of the core selling points of air conditioners. Therefore, high-efficiency dual-purpose air conditioners are not only a window for manufacturers to showcase their technological strength, but also a key factor in enhancing product market competitiveness. The refrigerant charge is a factor affecting air conditioner energy efficiency, influenced by factors such as operating conditions and system configuration. The optimal refrigerant charge required for dual-purpose air conditioners to achieve optimal performance in cooling and heating modes differs. Generally, the optimal refrigerant charge for heating mode is 5% to 30% higher than that for cooling mode. However, the refrigerant charge of existing air conditioning products cannot be adjusted according to changes in operating conditions. Therefore, the refrigerant charge is often not at the optimal point for system performance, resulting in suboptimal air conditioner energy efficiency.

[0045] Please refer to this document for details. Figures 3 to 8 This application provides an air conditioner 100, including a compressor 10, an outdoor heat exchanger 20, a liquid receiver 30, and an indoor heat exchanger 40. A partition 38 is provided inside the liquid receiver 30, dividing the inner cavity of the liquid receiver 30 into a first chamber 35 and a second chamber 36. The partition 38 is movable to change the volume of the first chamber 35 and the second chamber 36. The compressor 10, the outdoor heat exchanger 20, the first chamber 35, and the indoor heat exchanger 40 are sequentially connected to form a refrigerant circulation path. The second chamber 36 is also connected to the exhaust port of the compressor 10, so that the volume of the second chamber 36 can be adjusted by the exhaust of the compressor 10.

[0046] It should be noted that the compressor 10, the outdoor heat exchanger 20, the first chamber 35, and the indoor heat exchanger 40 are sequentially connected to form a refrigerant circulation path. Please refer to [link / reference]. Figure 1 In cooling mode, the refrigerant flowing from compressor 10 undergoes heat exchange through outdoor heat exchanger 20, then flows through the first chamber 35 and indoor heat exchanger 40, and finally returns to compressor 10. In heating mode, please refer to... Figure 2 The refrigerant flowing from the compressor 10 first flows to the indoor heat exchanger 40, then through the first chamber 35 and the outdoor heat exchanger 20, and finally flows back to the compressor 10. The first chamber 35 is located in the refrigerant circulation path. When the air conditioner 100 switches between cooling and heating modes, the rate of change in the refrigerant storage in the first chamber 35 is faster due to the impact of the refrigerant flow rate within the refrigerant circulation path. The second chamber 36 can be located in the refrigerant circulation path, for example... Figure 3 and Figure 4 In a corresponding embodiment, it may also be located outside the refrigerant circulation path, for example... Figure 9 and Figure 10The corresponding implementation methods are not limited here.

[0047] It should be emphasized that the refrigerant discharged from the exhaust port of the compressor 10 can flow directly to the control valve, and then to the indoor heat exchanger 40 or the outdoor heat exchanger 20. Alternatively, it can first flow to the second chamber 36 and then to the four-way valve, and then to the indoor heat exchanger 40 or the outdoor heat exchanger 20. Correspondingly, the second chamber 36 can be connected only to the exhaust port of the compressor 10, or it can be connected to both the exhaust port of the compressor 10 and the four-way valve. No limitation is made here.

[0048] Furthermore, the partition 38 divides the inner cavity of the reservoir 30 into a first chamber 35 and a second chamber 36. The sum of the volumes of the first chamber 35 and the second chamber 36 can be the volume of the inner cavity, so that when the position of the partition 38 changes, the volumes of the first chamber 35 and the second chamber 36 change accordingly.

[0049] In this embodiment, the compressor 10, the outdoor heat exchanger 20, the first chamber 35, and the indoor heat exchanger 40 are sequentially connected to form a refrigerant circulation path. The second chamber 36 is also connected to the exhaust port of the compressor 10, meaning the pressure in the second chamber 36 can be considered similar to the pressure at the exhaust port of the compressor 10. In cooling mode, the pressure in the first chamber 35 can be approximated as being approximately the same as the pressure at the refrigerant outlet of the outdoor heat exchanger 20. Due to the flow resistance encountered by the refrigerant in the heat exchanger during condensation, the condensation outlet pressure will be slightly lower than the exhaust pressure. Therefore, at the beginning of the cooling mode, the pressure in the first chamber 35 will be less than the pressure in the second chamber 36, releasing... A small portion of the refrigerant enters the refrigeration cycle. In heating mode, the pressure in the first chamber 35 can be approximated as equal to the pressure at the refrigerant inlet of the indoor heat exchanger 40. Since the refrigerant inlet of the indoor heat exchanger 40 is much smaller than the discharge pressure of the compressor 10, at the beginning of heating mode, the pressure in the first chamber 35 will be much smaller than the pressure in the second chamber 36. Under the pressure difference, the baffle 38 increases the volume of the second chamber 36 and decreases the volume of the first chamber 35, thereby releasing the refrigerant stored in the first chamber 35 into the heating cycle to a great extent, so that there is more refrigerant in the circulation path in heating mode than in the circulation path in cooling mode.

[0050] Furthermore, it is important to emphasize that, in the technical solution of this application, taking R32 refrigerant and a volume of 100ml in the first chamber 35 of the receiver 30 as an example, the density of the subcooled liquid refrigerant downstream of the outdoor heat exchanger 20 in cooling mode is approximately 900–930 kg / m³, while the density of the gas-liquid two-phase refrigerant upstream of the outdoor heat exchanger 20 in heating mode is approximately 100–150 kg / m³. The receiver 30 can store 90–93g of liquid in cooling mode and 10–15g in heating mode. Therefore, the amount of refrigerant participating in the circulation is greater in heating mode than in cooling mode.

[0051] Please refer to this carefully. Figures 1 to 4 In some embodiments, the air conditioner 100 further includes a first control valve 70; the first control valve 70 is connected to the indoor heat exchanger 40, the outdoor heat exchanger 20, the exhaust port of the compressor 10, and the intake port of the compressor 10, respectively.

[0052] In this embodiment, for details, please refer to... Figure 1 In cooling mode, the refrigerant flowing out of the exhaust port of the compressor 10 is guided by the first control valve 70 to the outdoor heat exchanger 20 for heat exchange, then flows into the first chamber 35 of the liquid receiver 30, and after heat exchange in the indoor heat exchanger 40, it flows back to the suction port of the compressor 10 via the first control valve 70.

[0053] Please see Figure 2 In heating mode, the refrigerant flowing out of the exhaust port of the compressor 10 is guided by the first control valve 70 to the indoor heat exchanger 40 for heat exchange, then flows into the first chamber 35 of the liquid receiver 30, and after heat exchange in the outdoor heat exchanger 20, it flows back to the suction port of the compressor 10 via the first control valve 70.

[0054] In the scheme of this embodiment, the first control valve 70 is directly connected to the exhaust port and the intake port of the compressor 10, so that at least part of the refrigerant flowing out of the exhaust port of the compressor 10 can be directly guided to the outdoor heat exchanger 20 or the indoor heat exchanger 40 through the first control valve 70, and its cooling and heating response is faster.

[0055] Furthermore, the volumes of the first chamber 35 and the second chamber 36 of the liquid receiver 30 in different modes will be described next. In some embodiments, the air conditioner 100 has a cooling mode divided into a low-load cooling mode and a high-load cooling mode. First, please refer to... Figure 5 , Figure 5This is an internal structural diagram of the liquid receiver 30 when the compressor 10 is off. At this time, the volume of the second chamber 36 is much smaller than the volume of the first chamber 35.

[0056] Under single cooling conditions, the optimal refrigerant charge required for low-load cooling mode is generally lower than that for high-load cooling mode.

[0057] Please refer to the following: Figure 6 , Figure 6 This is a diagram showing the internal structure of the receiver 30 of the air conditioner 100 in low-load cooling mode. Specifically, after the compressor 10 starts, the compressor 10 generates discharge pressure, compared to... Figure 5 In the state described above, under the action of the discharge pressure of the compressor 10, the partition 38 moves, and correspondingly, the volume of the second chamber 36 increases and the volume of the first chamber 35 decreases, thereby releasing a portion of the refrigerant for refrigeration cycle.

[0058] Next, please refer to Figure 7 , Figure 7 This is an internal structural diagram of the receiver 30 of the air conditioner 100 in the high-load cooling mode. In the high-load cooling mode, the compressor 10 has a larger load and a larger discharge pressure, which in turn makes the pressure in the second chamber 36 greater. The volume of the first chamber 35 is smaller than that in the low-load cooling mode, allowing more refrigerant to participate in the refrigeration cycle.

[0059] Please see Figure 8 , Figure 8 This is an internal structural diagram of the liquid receiver 30 of the air conditioner 100 in heating mode. Correspondingly, in heating mode, the discharge pressure of the compressor 10 is much greater than the pressure at the refrigerant inlet of the outdoor heat exchanger 20. Therefore, the volume of the second chamber 36 is much greater than the volume of the first chamber 35, thereby allowing more refrigerant to participate in the heating cycle.

[0060] It should be noted that the second chamber 36 may be located in the refrigerant circulation path, so that the refrigerant flowing out of the compressor 10 also needs to circulate through the second chamber 36. Of course, it may also be located outside the refrigerant circulation path, which is not limited here.

[0061] In some embodiments, the exhaust port of the compressor 10 is connected to the second chamber 36 via a capillary tube 60. Corresponding to the scheme in this embodiment, when the second chamber 36 is not located in the refrigerant circulation path, connecting the exhaust port of the compressor 10 and the second chamber 36 via the capillary tube 60 can prevent the liquid refrigerant flowing out of the compressor 10 from entering the second chamber 36, but the exhaust pressure of the compressor 10 can still be transmitted to the second chamber 36.

[0062] Please refer to the following: Figures 9 to 11 In some other embodiments, the second chamber 36 may be located in the refrigerant circulation path. Specifically, the liquid receiver 30 may have a third interface 33 and a fourth interface 34 connected to the second chamber 36, wherein the third interface 33 is connected to the exhaust port of the compressor 10; the air conditioner 100 also includes a second control valve 80, which is connected to the indoor heat exchanger 40, the outdoor heat exchanger 20, the fourth interface 34 and the suction port of the compressor 10, respectively.

[0063] In this embodiment, during cooling or heating mode, the refrigerant flowing out of the compressor 10 discharge port first flows entirely into the second chamber 36, and then through the second control valve 80, is guided to the indoor heat exchanger 40 or the outdoor heat exchanger 20. At this time, the refrigerant flowing out of the compressor 10 will be guided into the second chamber 36. Therefore, the pressure change in the second chamber 36 will be faster, thereby changing the volume of the first chamber 35 and the second chamber 36 more quickly.

[0064] Furthermore, it should be emphasized that in this embodiment, the third interface 33 is connected to the exhaust port of the compressor 10, which can be done using a common refrigerant pipe, so that the refrigerant discharged from the exhaust port of the compressor 10 can smoothly enter the second chamber 36.

[0065] For details, please refer to the following: Figure 9 In cooling mode, the refrigerant flowing out of the compressor 10 first flows into the second chamber 36, and then flows out of the second chamber 36 and is conducted to the outdoor heat exchanger 20 through the second control valve 80. After heat exchange, it flows through the first chamber 35 and the indoor heat exchanger 40. After heat exchange, it is then conducted to the suction port of the compressor 10 through the second control valve 80.

[0066] Please refer to the following instructions in heating mode. Figure 10In heating mode, the refrigerant flows into the second chamber 36 first, and then flows out of the second chamber 36 and is connected to the indoor heat exchanger 40 via the second control valve 80. After heat exchange, it flows through the first chamber 35 and the outdoor heat exchanger 20. After heat exchange, it is then connected to the suction port of the compressor 10 via the second control valve 80.

[0067] It should be noted that the specific implementation of the first control valve 70 and the second control valve 80 is not limited. They can be a combination of multiple three-way valves, or a four-way valve, or a six-way valve, a seven-way valve, etc., and are not limited here.

[0068] Please see Figures 5 to 8 Because the discharge pressure of the compressor 10 is too high, it is easy to compress the volume of the first chamber 35 to a relatively small size in the cooling mode. Alternatively, the partition 38 may not automatically reset after the compressor 10 is turned off. Therefore, in some embodiments, an elastic element 37 is provided in the first chamber 35 and / or the second chamber 36. One end of the elastic element 37 is connected to the partition 38 to provide resistance to the movement of the partition 38 when the partition 38 increases the volume of the second chamber 36.

[0069] In the scheme of this embodiment, one end of the elastic member 37 is connected to the partition 38, so that when the partition 38 increases the volume of the second chamber 36, it can provide resistance to the movement of the partition 38, thereby neutralizing part of the exhaust pressure and preventing the first chamber 35 from being compressed to a small volume in the cooling mode. After the compressor 10 is turned off, the partition 38 can be reset by the elastic force of the elastic member 37 itself.

[0070] Specifically, after the compressor 10 starts working, it generates exhaust pressure, and the pressure in the second chamber 36 increases. At this time, it is necessary to overcome the resistance of the elastic element 37 first, and then the partition 38 moves, increasing the volume of the second chamber 36 and decreasing the volume of the first chamber 35. After the compressor 10 stops working, the pressure in the second chamber 36 decreases accordingly, and the partition 38 will reset under the action of the elastic element 37, decreasing the volume of the second chamber 36 and increasing the volume of the first chamber 35.

[0071] It should be noted that the elastic element 37 can be disposed in the first chamber 35, the second chamber 36, or both chambers; no limitation is made here. When the elastic element 37 is disposed in the first chamber 35 and the compressor 10 is operating, the elastic element 37 is a compression elastic element 37. When the elastic element 37 is disposed in the second chamber 36 and the compressor 10 is operating, it is a tension elastic element 37. When the compressor 10 is not operating, the elastic element 37 can also be in a natural state.

[0072] The optimal refrigerant charge required for a dual-purpose air conditioner to achieve its best performance differs between cooling and heating modes. Generally, the optimal refrigerant charge in heating mode is 5% to 30% higher than that in cooling mode.

[0073] Therefore, in some embodiments, the air conditioner 100 has a heating mode and a cooling mode; when the air conditioner 100 is in heating mode, the volume of the first chamber 35 is a, and when the air conditioner 100 is in cooling mode, the volume of the first chamber 35 is b, wherein a < b.

[0074] In the scheme of this embodiment, since a < b, the volume of the first chamber 35 is smaller in heating mode than in cooling mode. Therefore, in heating mode, more refrigerant can participate in the circulation, thereby improving the heating effect of the air conditioner 100.

[0075] In a further embodiment, a is 5% to 30% smaller than b, thereby enabling the optimal refrigerant charge in heating mode.

[0076] In addition, in some embodiments, the liquid reservoir 30 also has a first interface 31 and a second interface 32 connected to the first chamber 35; the first interface 31 is connected to the outdoor heat exchanger 20, and the second interface 32 is connected to the indoor heat exchanger 40.

[0077] In cooling mode, refrigerant flows from the first port 31 into the first chamber 35 from the outdoor heat exchanger 20, then flows out from the second port 32, flows to the indoor heat exchanger 40, and then flows back to the suction port of the compressor 10 via the control valve. In heating mode, refrigerant flows from the second port 32 into the first chamber 35 from the indoor heat exchanger 40, then flows out from the first port 31, flows to the outdoor heat exchanger 20, and then flows back to the suction port of the compressor 10 via the control valve.

[0078] It should be noted that the second interface 32 is connected to the indoor heat exchanger 40. Alternatively, the second interface 32 can be directly connected to the indoor heat exchanger 40, or it can be indirectly connected through the throttling component 50, etc., which are not limited here.

[0079] Specifically, the shape of the first chamber 35 is not limited and can be any shape. In some embodiments, the first chamber 35 is tapered at the opening end near the first interface 31 and / or the second interface 32 to facilitate the flow of refrigerant in and out.

[0080] In a further embodiment, the first interface 31 and the second interface 32 are arranged opposite each other in the vertical direction, and the first interface 31 is located below the second interface 32.

[0081] In this embodiment, during cooling mode, the subcooled liquid refrigerant flows in through the first port 31 located below and flows out through the second port 32 located above. When the system starts cooling or switches from heating mode to cooling mode, the refrigerant gas in the first chamber 35 can be quickly discharged from the second port 32 located above under the combined action of the upward-moving refrigerant and the upward buoyancy of the gas, so that the first chamber 35 quickly reaches a liquid-filled state and the liquid storage volume increases rapidly.

[0082] In heating mode, the gas-liquid two-phase refrigerant flows in through the upper second port 32 and flows out through the lower first port 31. When the system starts heating or switches from cooling mode to heating mode, the refrigerant liquid in the first chamber 35 can be quickly discharged from the lower first port 31 under the combined action of the downward moving refrigerant and the downward liquid gravity, which causes the dryness of the gas-liquid two-phase refrigerant in the first chamber 35 to increase rapidly, the density to decrease, and the liquid storage volume to decrease rapidly.

[0083] For further details, please refer to Figures 12 to 13 In some embodiments, the first chamber 35 includes a first interface 31, an upper connecting section 311, a liquid storage section 312, a lower connecting section 313, and a second interface 32 arranged sequentially from top to bottom. The cutting lines of the upper connecting section 311 and the lower connecting section 313 can be straight or curved, and are not limited here.

[0084] In cooling mode, since the upper connecting section 311 is designed with an upward sloping profile, when the system operating conditions fluctuate and the outlet of the outdoor heat exchanger 20 is not completely subcooled, the air bubbles entering the first chamber 35 are more likely to be discharged from the first interface 31, and are less likely to accumulate in the first chamber 35, thus reducing the amount of refrigerant stored.

[0085] In heating mode, because the lower connecting section 313 has a downward sloping profile, when the refrigerant enters from the top and exits from the bottom, liquid accumulation in the receiver 30 is not likely to occur, thus ensuring a lower refrigerant storage capacity.

[0086] In some embodiments, in order to throttle and reduce the pressure of the refrigerant, a throttling component 50 is also provided in the refrigerant circulation path. The throttling component 50 is disposed between the second port 32 of the liquid receiver 30 and the indoor heat exchanger 40, so that in the cooling mode, the refrigerant flowing out of the outdoor heat exchanger 20 is throttled and reduced in pressure, and in the heating mode, the refrigerant flowing out of the indoor heat exchanger 40 is throttled and reduced in pressure.

[0087] Specifically, the form of the throttling component 50 is not limited. It may include only a throttling valve, or it may also include a filter. In some embodiments, the throttling component 50 includes a first filter 51, a throttling valve 52, and a second filter 53 arranged in sequence. The first filter 51 is connected to the second interface 32, and the second filter 53 is connected to the indoor heat exchanger 40.

[0088] In this embodiment, by setting the first filter 51 and the second filter 53, the refrigerant flowing into and out of the throttle 52 can be filtered regardless of whether it is in cooling mode or heating mode, thereby preventing the throttle 52 from becoming blocked.

[0089] The air conditioner provided in the embodiments of this application has been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of this application. The description of the above embodiments is only for the purpose of helping to understand the method and core ideas of this application. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the ideas of this application. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. An air conditioner, characterized in that, Includes compressor, outdoor heat exchanger, liquid receiver and indoor heat exchanger; The liquid reservoir is provided with a partition, which divides the inner cavity of the liquid reservoir into a first chamber and a second chamber, and the partition is movable to change the volume of the first chamber and the second chamber; The compressor, the outdoor heat exchanger, the first chamber, and the indoor heat exchanger are sequentially connected to form a refrigerant circulation path; The second chamber is also connected to the exhaust port of the compressor so that the volume of the second chamber can be adjusted by the exhaust of the compressor.

2. The air conditioner according to claim 1, characterized in that, The air conditioner also includes a first control valve; The first control valve is connected to the indoor heat exchanger, the outdoor heat exchanger, the exhaust port of the compressor, and the intake port of the compressor, respectively.

3. The air conditioner according to claim 1, characterized in that, The compressor's exhaust port is connected to the second chamber via a capillary tube.

4. The air conditioner according to claim 1, characterized in that, The liquid reservoir has a third interface and a fourth interface that communicate with the second chamber, wherein the third interface is connected to the exhaust port of the compressor; The air conditioner also includes a second control valve, which is connected to the indoor heat exchanger, the outdoor heat exchanger, the fourth interface, and the air intake of the compressor.

5. The air conditioner according to any one of claims 1 to 4, characterized in that, The first chamber and / or the second chamber are provided with elastic elements; One end of the elastic element is connected to the partition to provide resistance to the movement of the partition when the partition increases the volume of the second chamber.

6. The air conditioner according to any one of claims 1 to 4, characterized in that, The air conditioner has a heating mode and a cooling mode; When the air conditioner is in heating mode, the volume of the first chamber is a, and when the air conditioner is in cooling mode, the volume of the first chamber is b, where a < b.

7. The air conditioner according to claim 1, characterized in that, The liquid reservoir also has a first interface and a second interface that communicate with the first chamber. The first interface is connected to the outdoor heat exchanger, and the second interface is connected to the indoor heat exchanger.

8. The air conditioner according to claim 7, characterized in that, A throttling component is also provided in the refrigerant circulation path, and the throttling component is located between the second interface of the liquid receiver and the indoor heat exchanger.

9. The air conditioner according to claim 8, characterized in that, The throttling assembly includes a first filter, a throttler, and a second filter arranged in sequence, wherein the first filter is connected to the second interface, and the second filter is connected to the indoor heat exchanger.

10. The air conditioner according to claim 7, characterized in that, The first interface and the second interface are positioned opposite each other in the vertical direction, with the first interface located below the second interface.

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