Suction structure, compressor and air conditioner
By designing a flat, elongated suction port and a smoothly transitioned suction pipe connection section, the problems of low resistance and small closing angle in the suction structure of rotary compressors are solved, thereby improving the volumetric efficiency and cooling or heating capacity of the compressor.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- QINGDAO HAIER AIR CONDITIONER GENERAL CORP LTD
- Filing Date
- 2026-04-07
- Publication Date
- 2026-07-31
AI Technical Summary
The circular suction port of existing rotary compressors makes it difficult to simultaneously achieve both low suction resistance and a small suction closing angle, resulting in reduced compressor volumetric efficiency.
The system employs a flat, elongated suction port with its width direction corresponding to the suction closing direction. A smooth transition is achieved through the design of the suction pipe connection section, optimizing the suction structure to reduce flow loss.
It improves the volumetric efficiency of the compressor, enhances the flow area and continuity of the refrigerant gas, reduces flow resistance, and improves cooling or heating capacity.
Smart Images
Figure CN122485818A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of air conditioner technology, specifically providing an air intake structure, a compressor, and an air conditioner. Background Technology
[0002] In the refrigeration field, compressors can be divided into reciprocating compressors, rotary compressors, and scroll compressors. Among them, rotary compressors use rollers that rotate eccentrically inside the cylinder to compress fluids and are widely used in refrigeration (heating) cycle systems such as refrigerators, air conditioners, freezers, and heat pump water heaters.
[0003] The suction structure of a conventional rotary compressor includes a suction port and a suction pipe. A circular suction port is located on the side wall of the cylinder. One end of the suction pipe connects to the outlet pipe of the liquid receiver, and the other end is inserted into the suction port. Low-temperature, low-pressure refrigerant gas from the liquid receiver enters the suction chamber of the cylinder through the outlet pipe, suction pipe, and suction port. The structural parameters of the suction port are directly geometrically related to the compressor's suction closing angle. The suction closing angle refers to the angle rotated by the crankshaft from the moment the rollers close the suction port until the start of the compression process. If the suction closing angle is too large, high-pressure gas will flow back into the liquid receiver through the suction port, resulting in significant backflow losses and reduced compressor volumetric efficiency.
[0004] A larger diameter of the circular suction orifice results in a larger suction closing angle, increasing backflow losses and reducing compressor volumetric efficiency. Conversely, a smaller diameter results in a smaller suction closing angle and reduced backflow losses. However, a smaller orifice leads to increased refrigerant velocity and flow resistance, causing suction pressure loss and reducing the amount of refrigerant entering the cylinder, which also reduces compressor volumetric efficiency. Therefore, a circular suction orifice cannot simultaneously achieve the dual optimization goals of low suction resistance and a small suction closing angle, thus hindering the improvement of compressor volumetric efficiency.
[0005] Accordingly, the field needs a new intake structure, compressor, and air conditioner to solve the above problems. Summary of the Invention
[0006] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problem that it is difficult for a circular air intake hole to simultaneously achieve the dual optimization goals of low air intake resistance and small air intake closing angle, which affects the improvement of compressor volumetric efficiency.
[0007] In a first aspect, the present invention provides an air intake structure; the air intake structure is applied to a cylinder, the cylinder having an air intake chamber, the air intake structure including an air intake hole, the air intake hole being disposed on the side wall of the cylinder and communicating with the air intake chamber; The cross-section of the air intake hole is designed as a flat and elongated hole. The height and width directions of the cross-section of the air intake hole are perpendicular to each other. The height of the cross-section of the air intake port is greater than its width, and the width direction corresponds to the air intake closing direction of the cylinder.
[0008] When the above technical solution is adopted, the cross-section of the suction port is set to be a flat and elongated shape, and its width direction corresponds to the suction closing direction. Compared with a circular suction port, when the width of the suction port with a flat and elongated cross-section is the same as the diameter of the suction port with a circular cross-section, the suction port has a larger effective flow area. By designing the width and height of the suction port with a flat and elongated cross-section, a larger effective flow area can be achieved while ensuring that the suction port has a small size. This avoids the backflow loss of high-pressure gas caused by an excessively large suction closing angle and reduces the suction pressure loss caused by an excessively small orifice diameter, thereby effectively improving the volumetric efficiency of the compressor.
[0009] In the preferred embodiment of the above-mentioned air intake structure, the cross-section of the air intake hole is set as an elliptical hole, an oblong hole, a rectangular hole, or a U-shaped hole; and / or The aspect ratio of the air intake hole is 1.09-2.5.
[0010] When the above technical solution is adopted, the cross-section of the air intake hole is set as an elliptical hole, a waist-shaped hole, a rectangular hole, or a U-shaped hole. These shapes of holes have a larger area when the width is the same as the diameter of the circular hole, and are easy to process and manufacture.
[0011] The aspect ratio of the intake port is 1.09-2.5. Within this range, the structural strength of the intake port can be improved, and the matching relationship between the flow area of the intake port and the size of the intake closing direction can be further optimized. While ensuring sufficient intake volume, the intake closing angle can be minimized to the greatest extent, thereby further optimizing the volumetric efficiency of the compressor.
[0012] In the preferred embodiment of the above-mentioned intake structure, the axis of the intake hole is perpendicular to the axis of the cylinder.
[0013] With the above technical solution, the intake port axis is perpendicular to the cylinder axis, so that the refrigerant gas enters the intake chamber along the shortest radial path of the cylinder, reducing the additional flow loss caused by airflow deflection due to the tilted setting.
[0014] In a preferred embodiment of the above-described suction structure, the suction structure further includes a suction pipe, one end of which is connected to the outlet pipe of the gas-liquid separator, and the other end of which is connected to the suction port. The refrigerant gas in the gas-liquid separator enters the suction chamber through the outlet pipe, the suction pipe, and the suction port; and / or The air inhalation tube includes a first connecting section and a second connecting section. The air outlet tube is connected to the first connecting section. The first end of the second connecting section is connected to the first connecting section. The second end of the second connecting section is inserted into the air inhalation hole. The connection between the first connecting segment and the second connecting segment is a continuous and smooth transition, and the inner diameter of the second connecting segment gradually decreases from the first end to the second end.
[0015] With the above technical solution, the connection between the first connecting section and the second connecting section is continuous and smooth. The inner diameter of the second connecting section gradually decreases from the first end to the second end, which enables the refrigerant gas to smoothly transition from the outlet pipe to the flat and elongated suction hole. This can reduce the eddy currents and local resistance losses caused by the abrupt change in cross-section, reduce the flow resistance in the suction pipe, thereby increasing the amount of refrigerant entering the suction chamber and improving the volumetric efficiency of the compressor.
[0016] In the preferred embodiment of the above-mentioned air intake structure, the cross-sectional shape of the first connecting section matches the cross-sectional shape of the air outlet pipe; The cross-sectional shape of the second connecting segment matches the cross-sectional shape of the first connecting segment; or The cross-sectional shape of the second end of the second connecting segment matches the cross-sectional shape of the air intake.
[0017] When using the above technical solution, the cross-section of the outlet pipe is usually circular and larger than the cross-sectional area of the suction port. The first connecting section matches the outlet pipe of the gas-liquid separator, facilitating connection between the first connecting section and the outlet pipe. The second end of the second connecting section matches the suction port, facilitating insertion into the suction port.
[0018] In the preferred embodiment of the above-mentioned air intake structure, the cross-section of the second end of the second connecting segment is set as an elliptical hole, and the wall thickness corresponding to the height direction of the second connecting segment is greater than the wall thickness corresponding to the width direction of the second connecting segment.
[0019] When using the above technical solution, the cross-section of the second connecting section is set as an elliptical hole. This shape can reduce the flow resistance of the second connecting section, but it will also cause stress concentration in the height direction. Making the wall thickness of the second connecting section in the height direction greater than the wall thickness in the width direction can improve the strength of the second connecting section in the height direction, thereby improving the reliability and durability of the suction pipe connection. Furthermore, since the wall thickness in the width direction of the second connecting section is not increased, the width of the suction hole is not increased, thus the suction closing angle is not increased.
[0020] In the preferred embodiment of the above-described air intake structure, given the effective flow areas of the first and second ends of the second connecting segment, the length of the second connecting segment can be calculated using the following formula: in, : The length of the second connecting segment; Correction system, with a value range of 0.02-0.05; : The effective flow area at the first end of the second connecting section; : The effective flow area at the second end of the second connecting section.
[0021] With the above technical solution, the first end of the second connecting section mates with the outlet pipe, and the cross-section of the outlet pipe is determined, thus determining the effective flow area of the first end of the second connecting section. The area of the suction port is related to parameters such as the suction closing angle, the height-to-width ratio of the suction port, and the structural dimensions of the cylinder. The second end of the second connecting section mates with the suction port, and the effective flow area of the second end of the second connecting section is determined after the size of the suction port is determined. Given the effective flow areas of the first and second ends of the second connecting section, the optimal length of the second connecting section can be calculated using a formula. This ensures the smoothest transition of the flow channel from a circular cross-section to a flat, elongated cross-section, allowing the refrigerant gas to flow close to the pipe wall during flow, reducing boundary layer separation and eddy current generation, thereby achieving minimal flow loss.
[0022] In the preferred embodiment of the above-mentioned air intake structure, the air intake hole includes an inlet section and an intake section connected end to end, the second end of the second connecting section is inserted into the inlet section, and the inner diameter of the second end of the second connecting section is the same as the inner diameter of the air intake hole.
[0023] By employing the above technical solution, and dividing the suction port into an inlet section and an intake section, and ensuring that the inner diameter of the second end of the second connecting section of the suction pipe matches the inner diameter of the suction port, a smooth connection between the suction pipe and the inner wall of the intake section is achieved. Compared to directly inserting the second connecting section into the suction port, this eliminates the step at the connection point, preventing sudden expansion or contraction losses in the airflow at the connection point. This further improves the continuity of the entire flow path from the suction pipe to the suction port, reduces refrigerant gas loss along the flow path, and increases the amount of refrigerant entering the suction chamber.
[0024] In a second aspect, the present invention also provides a compressor; the compressor includes the suction structure described above.
[0025] When the above technical solution is adopted, the flat and elongated suction hole can take into account both the suction closing angle and the effective flow area of the suction hole, reduce the backflow loss of high pressure gas caused by excessive suction closing angle, and reduce the suction pressure loss caused by excessively small hole diameter. This can effectively improve the volumetric efficiency of the compressor, so that the compressor has a higher cooling or heating capacity under the same displacement and operating conditions.
[0026] Thirdly, the present invention also provides an air conditioner; the air conditioner includes the compressor described above.
[0027] When the above technical solution is adopted, the air conditioner compressor has a higher volumetric efficiency, which enables the air conditioner to have a higher cooling or heating capacity under the same displacement and operating conditions, thereby improving the user experience.
[0028] In summary, the present invention has at least the following beneficial effects: 1. By designing the cross-section of the suction port as a flat and elongated shape, and aligning its width with the suction closing direction, the suction port with a flat and elongated cross-section has a larger effective flow area when its width is the same as that of a circular suction port. By designing the width and height of the suction port with a flat and elongated cross-section, a larger effective flow area can be achieved while maintaining a smaller size. This avoids high-pressure gas backflow losses caused by an excessively large suction closing angle and reduces suction pressure losses caused by an excessively small orifice diameter, thereby effectively improving the volumetric efficiency of the compressor.
[0029] 2. The connection between the first connecting section and the second connecting section is continuous and smooth. The inner diameter of the second connecting section gradually decreases from the first end to the second end, which allows the refrigerant gas to smoothly transition from the outlet pipe to the flat and elongated intake hole. This can reduce the eddy currents and local resistance losses caused by the abrupt change in cross-section, reduce the flow resistance in the intake pipe, thereby increasing the amount of refrigerant entering the intake chamber and improving the volumetric efficiency of the compressor.
[0030] 3. Given the effective flow areas of the first and second ends of the second connecting section, the optimal length of the second connecting section can be calculated using a formula. This ensures that the flow path of the second connecting section changes most smoothly from a circular cross-section to a flat and elongated cross-section, allowing the refrigerant gas to flow along the pipe wall during the flow process, reducing boundary layer separation and eddy current generation, thereby achieving minimal flow loss. Attached Figure Description
[0031] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which: Figure 1 This is a schematic diagram of the compressor of the present invention; Figure 2 This is a cross-sectional view of the cylinder of the present invention; Figure 3 This is a schematic diagram of the second connecting segment of the present invention.
[0032] Figure label: 1. Cylinder; 21. Intake port; 211. Inlet section; 212. Intake section; 22. Intake pipe; 221. First connecting section; 222. Second connecting section; 3. Gas-liquid separator; 4. Outlet pipe. Detailed Implementation
[0033] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the invention and are not intended to limit the scope of protection of the invention. Those skilled in the art can make adjustments as needed to adapt to specific applications.
[0034] It should be noted that in the description of this invention, terms such as "upper," "lower," "left," and "right," indicating directional or positional relationships, are based on the directional or positional relationships shown in the accompanying drawings. These are 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 invention. Furthermore, the terms "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.
[0035] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "connected" should be interpreted broadly. For example, they can refer to a fixed connection or a detachable connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.
[0036] To address the issue that a circular intake port cannot simultaneously achieve the dual optimization goals of low intake resistance and a small intake closing angle, thus affecting the improvement of compressor volumetric efficiency.
[0037] like Figure 1 and Figure 2As shown, this embodiment discloses an air conditioner, which includes a compressor. The compressor includes a gas-liquid separator 3, a cylinder 1, a roller (not shown), a sliding vane (not shown), and a suction structure. The gas-liquid separator 3 is used to separate liquid refrigerant and refrigerant gas. In this embodiment, the gas-liquid separator 3 is a liquid storage tank. The refrigerant gas separated from the liquid storage tank enters the cylinder 1 through the outlet pipe 4 of the liquid storage tank and the suction structure. The sidewall of the cylinder 1 is formed into a ring. The roller is rotatably installed inside the cylinder 1, and the sliding vane is also located inside the cylinder 1 and is retractably pressed against the roller. When the roller makes an eccentric rotational motion inside the cylinder 1, a crescent-shaped space is formed between the outer wall of the roller and the sidewall of the cylinder 1. The crescent-shaped space is divided into a suction chamber and a compression chamber by the sliding vane. The suction chamber is located on the suction side of the sliding vane and is used to contain the low-pressure refrigerant gas entering from the suction structure. The compression chamber is located on the exhaust side of the sliding vane and is used to compress the refrigerant gas.
[0038] like Figures 1 to 3 As shown, specifically, the intake structure includes an intake port 21 and an intake pipe 22. The intake port 21 is located on the side wall of the cylinder 1 and communicates with the intake chamber. One end of the intake pipe 22 is connected to the outlet pipe 4, and the other end of the intake pipe 22 is connected to the intake port 21. The refrigerant gas separated from the liquid storage tank enters the intake chamber through the outlet pipe 4, the intake pipe 22, and the intake port 21. The cross-section of the intake port 21 is designed as a flat and elongated hole. The height and width directions of the cross-section of the intake port 21 are perpendicular to each other. The height h of the intake port cross-section is greater than the width w, and the width direction corresponds to the intake closing direction of the cylinder 1.
[0039] By designing the cross-section of the suction port 21 as a flat, elongated shape, with its width direction corresponding to the suction closing direction, the suction port 21 with a flat, elongated cross-section has a larger effective flow area compared to a circular suction port 21, provided the width is the same as the diameter of a circular suction port 21. Conversely, when the effective flow area of the suction port 21 with a flat, elongated cross-section is the same as that of a circular suction port 21, the suction port with a flat, elongated cross-section has a smaller suction closing angle. By designing the width and height of the suction port 21 with a flat, elongated cross-section, a larger effective flow area can be achieved while maintaining a smaller overall size. This avoids high-pressure gas backflow losses caused by an excessively large suction closing angle and reduces suction pressure losses caused by an excessively small orifice diameter, thereby effectively improving the volumetric efficiency of the compressor.
[0040] like Figures 1 to 3As shown, the cross-section of the suction port 21 is set as an elliptical hole, a waist-shaped hole, a rectangular hole, or a U-shaped hole, and the height-to-width ratio of the suction port 21 is 1.09-2.5. When the width of the elliptical hole, waist-shaped hole, rectangular hole, or U-shaped hole is the same as the diameter of the circular hole, it has a larger area. When the height-to-width ratio of the suction port 21 is 1.09-2.5, the structural strength of the suction port 21 can be improved, and the matching relationship between the flow area of the suction port 21 and the dimensions in the suction closing direction can be further optimized. While ensuring sufficient air intake, the suction closing angle is reduced, thereby further optimizing the volumetric efficiency of the compressor. In this embodiment, the cross-section of the suction port 21 is set as an elliptical hole, and the internal contour of the suction port 21 is composed of a smooth curve. This reduces the possibility of refrigerant gas separating from the hole wall and forming eddies when flowing through the suction port 21, further reducing the flow loss of refrigerant gas and improving the volumetric efficiency of the compressor. The height-to-width ratio of the suction port 21 is 1.2. The flow area of the suction port 21 is optimally matched with the size of the suction closing direction. While ensuring sufficient air intake, the suction closing angle is minimized to the greatest extent, thereby further optimizing the volumetric efficiency of the compressor.
[0041] Furthermore, the axes of the intake port 21 and the intake pipe 22 are both perpendicular to the axis of the cylinder 1. The refrigerant gas enters the intake chamber along the shortest radial path of the cylinder 1, which reduces the airflow deflection and flow loss caused by the inclined and turning settings, and can increase the amount of refrigerant entering the intake chamber.
[0042] like Figures 1 to 3 As shown, the suction pipe 22 includes a first connecting section 221 and a second connecting section 222. The cross-sectional shape of the first connecting section 221 matches the cross-sectional shape of the exhaust pipe 4. The end of the exhaust pipe 4 furthest from the liquid storage tank is inserted into the first connecting section 221 and welded in place. The first end of the second connecting section 222 is connected to the first connecting section 221, and the second end of the second connecting section 222 is inserted into the suction hole 21 and welded in place. The shape of the first end face of the second connecting section 222 matches the cross-section of the first connecting section, and the cross-sectional shape of the second end of the second connecting section 222 matches the cross-section of the suction hole 21, so as to facilitate insertion into the suction hole. Of course, the cross-sectional shapes of both the first connecting section 221 and the second connecting section 222 can be set to match the cross-sectional shape of the suction hole 21, or the cross-sectional shapes of both the first connecting section 221 and the second connecting section 222 can be set to match the cross-sectional shape of the exhaust pipe 4.
[0043] The connection between the first connecting section 221 and the second connecting section 222 is continuous and smooth, and the inner diameter of the second connecting section 222 gradually decreases from the first end to the second end. The cross-sectional area of the outlet pipe 4 is usually larger than the cross-sectional area of the suction port 21. The continuous and smooth transition between the first connecting section 221 and the second connecting section 222, and the gradual decrease in the inner diameter of the second connecting section 222 from the first end to the second end, allows the refrigerant gas to smoothly transition from the outlet pipe 4 to the suction port 21. This reduces the eddy currents and local resistance losses caused by the abrupt change in cross-section, reduces the flow resistance in the suction pipe 22, thereby increasing the amount of refrigerant entering the suction chamber and improving the volumetric efficiency of the compressor.
[0044] In this embodiment, the cross-section of the outlet pipe 4 is circular and larger than the cross-sectional area of the intake port 21. The cross-section of the first connecting section 221 is circular and matches the outlet pipe 4, facilitating the insertion of the outlet pipe 4 into the first connecting section 221. The second connecting section 222 is integrally formed with the first connecting section 221. The first end of the second connecting section 222 is circular and matches the first connecting section 221, while the second end is elliptical and matches the intake port 21, facilitating the insertion of the second connecting section 222 into the intake port 21. The refrigerant gas enters the first connecting section 221 from the outlet pipe 4 with its circular cross-section, and then smoothly transitions to the second connecting section 222 and the intake port 21. This reduces the eddies and local resistance losses generated at the connection points of the first and second connecting sections 221 and 222, and at the connection point between the second connecting section 222 and the intake port 21, thereby reducing the flow resistance within the intake pipe 22 and increasing the amount of refrigerant entering the intake chamber, thus improving the compressor's volumetric efficiency.
[0045] Furthermore, the wall thickness of the second connecting segment 222 in the height direction is greater than the wall thickness in the width direction. The cross-sectional shape of the second connecting segment 222 matches the cross-sectional shape of the suction port 21, also being a flat, elongated shape. This causes stress concentration in the height direction of the second connecting segment 222. Increasing the wall thickness in the height direction of the second connecting segment 222 improves its strength in that direction, enhancing the reliability and durability of the suction pipe 22 connection. Simultaneously, since the wall thickness in the width direction of the second connecting segment 222 is not increased, the width of the suction port 21 is not increased, thus preventing an increase in the suction closing angle.
[0046] like Figures 1 to 3As shown, the first end of the second connecting section 222 mates with the exhaust pipe 4. Given the cross-section of the exhaust pipe 4, the effective flow area of the first end of the second connecting section 222 is determined. The area of the suction port 21 is related to parameters such as the suction closing angle, the height-to-width ratio of the suction port 21, and the structural dimensions of the cylinder 1. The second end of the second connecting section 222 mates with the suction port 21. Once the size of the suction port 21 is determined, the effective flow area of the second end of the second connecting section 222 is determined. Given the effective flow areas of the first and second ends of the second connecting section 222, the length of the second connecting section 222 can be calculated using the following formula: in, : The length of the second connecting segment 222; The correction system has a value range of 0.02-0.05, with 0.03 being the preferred value. : The effective flow area at the first end of the second connecting section 222; : The effective flow area at the second end of the second connecting section 222.
[0047] The optimal length of the second connecting segment can be calculated using the formula, so that the flow channel change from a circular cross-section to a flat and elongated cross-section in the second connecting segment 222 is as gradual as possible. This allows the refrigerant gas to flow along the pipe wall during the flow process, reducing boundary layer separation and eddy current generation, thereby achieving minimal flow loss.
[0048] like Figure 1 and Figure 2 As shown, the suction port 21 further includes an inlet section 211 and an intake section 212 connected end to end. The second end of the second connecting section 222 is inserted into the inlet section 211, and the inner diameter of the second end of the second connecting section 222 is the same as the inner diameter of the suction port 21. By dividing the suction port 21 into the inlet section 211 and the intake section 212, and making the inner diameter of the second end of the second connecting section 222 of the suction pipe 22 consistent with the inner diameter of the suction port 21, a smooth connection between the suction pipe 22 and the inner wall of the suction section is achieved. Compared with directly inserting the second connecting section 222 into the suction port 21, the step at the connection between the second connecting section 222 and the suction port 21 can be eliminated, avoiding the loss of sudden expansion or contraction of airflow at the connection, further improving the continuity of the entire flow channel from the suction pipe 22 to the suction port 21, reducing the friction loss of refrigerant gas, increasing the amount of refrigerant entering the suction chamber, and improving the volumetric efficiency of the compressor.
[0049] Improving the volumetric efficiency of a compressor allows it to have a higher cooling or heating capacity under the same displacement and operating conditions. This, in turn, enables air conditioners to have a higher cooling or heating capacity under the same displacement and operating conditions, or reduces energy consumption and improves the user experience under the same cooling or heating capacity.
[0050] The technical solution of the present invention has 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 the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, 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 the present invention.
Claims
1. An air intake structure applied to a cylinder (1), characterized in that, The cylinder (1) is provided with an air intake chamber, and the air intake structure includes an air intake hole (21), which is located on the side wall of the cylinder (1) and communicates with the air intake chamber. The cross-section of the air intake hole (21) is set as a flat elongated hole shape. The height direction and the width direction of the cross-section of the air intake hole (21) are perpendicular to each other. The height of the cross-section of the air intake port is greater than its width, and the width direction corresponds to the air intake closing direction of the cylinder (1).
2. The air intake structure according to claim 1, characterized by The cross-section of the air intake (21) is set as an elliptical hole, a waist-shaped hole, a rectangular hole, or a U-shaped hole; and / or The aspect ratio of the air intake hole (21) is 1.09-2.
5.
3. The air intake structure of claim 1, wherein The axis of the air intake hole (21) is perpendicular to the axis of the cylinder (1).
4. The air intake structure of claim 2, wherein The suction structure also includes a suction pipe (22), one end of which is connected to the outlet pipe (4) of the gas-liquid separator (3), and the other end of which is connected to the suction port (21). The refrigerant gas in the gas-liquid separator (3) enters the suction chamber through the outlet pipe (4), the suction pipe (22), and the suction port (21); and / or The air intake tube (22) includes a first connecting section (221) and a second connecting section (222). The air outlet tube (4) is connected to the first connecting section (221). The first end of the second connecting section (222) is connected to the first connecting section (221). The second end of the second connecting section (222) is inserted into the air intake hole (21). The connection between the first connecting segment (221) and the second connecting segment (222) is continuous and smooth, and the inner diameter of the second connecting segment (222) gradually decreases from the first end to the second end.
5. The air intake structure of claim 4, wherein The cross-sectional shape of the first connecting section (221) matches the cross-sectional shape of the air outlet pipe (4); The cross-sectional shape of the second connecting segment (222) matches the cross-sectional shape of the first connecting segment (221); or The cross-sectional shape of the second end of the second connecting segment (222) matches the cross-sectional shape of the air intake (21).
6. The air intake structure according to claim 5, characterized in that, The cross-section of the second end of the second connecting segment (222) is set as an elliptical hole, and the wall thickness of the second connecting segment (222) in the height direction is greater than the wall thickness of the second connecting segment (222) in the width direction.
7. The air intake structure according to claim 6, characterized in that, Given the effective flow areas of the first and second ends of the second connecting segment (222), the length of the second connecting segment (222) can be calculated using the following formula: ， in, : The length of the second connecting segment (222); Correction system, with a value range of 0.02-0.05; : The effective flow area at the first end of the second connecting section (222); : The effective flow area at the second end of the second connecting section (222).
8. The air intake structure according to claim 7, characterized in that, The air intake (21) includes an inlet section (211) and an intake section (212) connected end to end. The second end of the second connecting section (222) is inserted into the inlet section (211), and the inner diameter of the second end of the second connecting section (222) is the same as the inner diameter of the air intake (21).
9. A compressor, characterized in that, The compressor includes the suction structure as described in any one of claims 1-8.
10. An air conditioner, characterized in that, The air conditioner includes the compressor as described in claim 9.