Air cylinder structure and compressor

Abstract

The invention provides an air cylinder structure and a compressor, the air cylinder structure comprises a cylinder body, the cylinder body is internally provided with a compression cavity and an air suction port, one end of the air suction port is communicated with the compression cavity, and the other end of the air suction port is communicated to the outside of the cylinder body; the flange valve seat is connected with the cylinder body, an air outlet is formed in the flange valve seat, and the air outlet is communicated with the compression cavity; wherein the minimum distance between the axis of the air suction port and the flange valve seat is larger than the minimum distance between the axis of the air suction port and the end, away from the flange valve seat, of the cylinder body, and the technical effect that in the prior art, a compressor is low in energy efficiency is achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a cylinder structure and a compressor. Background Art

[0002] Compressor energy efficiency and cost are the areas that customers are most concerned about. With the improvement of existing technologies, small cylinder structures are often used to replace large cylinder structure compressors to achieve optimal cost. At the same time, in the cylinder structure of the existing technology, the center of the intake pipe is at the same height as the center plane of the cylinder, which brings the following problems: ① In the existing compressor structure, when the suction center distance is in the middle, the suction flow path evenly impacts the structures at the upper and lower ends of the cylinder. Due to the size of the impact received by the exhaust end, the thickness of the exhaust end flange valve seat cannot be further reduced, so the suction resistance and clearance volume cannot be reduced, and ultimately the compressor energy efficiency cannot be improved. ② Small cylinders are limited by the outer diameter of the cylinder body, and the displacement is often increased by increasing the cylinder height. In the multi-cylinder structure, the center distance between cylinders increases, and the liquid distributor of the large cylinder structure cannot be adapted, which increases the types of liquid distributors. The increase in the distance between the suction pipes affects the structural strength, and also increases the space of the liquid distributor, which is not conducive to a compact structure.

[0003] Therefore, the prior art needs to be further developed. Summary of the invention

[0004] The purpose of the present invention is to overcome the above technical deficiencies and provide a cylinder structure and a compressor to solve the technical problem of low energy efficiency of the compressor in the related art.

[0005] In order to achieve the above technical objectives, the present invention adopts the following technical cylinder structure of this embodiment: a cylinder structure is provided, including: A cylinder body, wherein the cylinder body has a compression chamber and an air intake port, one end of the air intake port is connected to the compression chamber, and the other end of the air intake port is connected to the outside of the cylinder body; A flange valve seat, the flange valve seat is connected to the cylinder body, an air outlet is arranged in the flange valve seat, and the air outlet is communicated with the compression chamber; Wherein, the minimum distance between the axis of the air intake port and the flange valve seat is greater than the minimum distance between the axis of the air intake port and an end of the cylinder body away from the flange valve seat.

[0006] Further, the cylinder body includes a first cylinder body and a second cylinder body; the flange valve seat includes a first flange valve seat and a second flange valve seat; the first cylinder body and the second cylinder body are both located between the first flange valve seat and the second flange valve seat; the first cylinder body is connected to the first flange valve seat, and the second cylinder body is connected to the second flange valve seat; a first compression chamber and a first air intake port communicating with the first compression chamber are provided in the first cylinder body; a second compression chamber and a second air intake port communicating with the second compression chamber are provided in the second cylinder body; Wherein, the minimum distance between the first air intake port and the first flange valve seat is greater than the minimum distance between the first air intake port and an end of the first cylinder body away from the first flange valve seat; the minimum distance between the second air intake port and the second flange valve seat is greater than the minimum distance between the second air intake port and an end of the second cylinder body away from the second flange valve seat.

[0007] Furthermore, the cylinder structure includes a partition plate, and the partition plate is located between the first cylinder body and the second cylinder body, so that the first cylinder body and the second cylinder body are spaced apart.

[0008] Furthermore, the cylinder structure also includes a crankshaft, which passes through the cylinder body and the flange valve seat; along the direction parallel to the axis of the crankshaft, the thickness of the partition is H2, the thickness of the first cylinder body is H1, the thickness of the second cylinder body is H6, the minimum thickness of the valve seat exhaust area in the first flange valve seat is H3, and the minimum thickness of the valve seat exhaust area of ​​the second flange valve seat is H4; wherein, H1>H2>H3, H6>H2>H4.

[0009] Further, the center distance between the first air intake port and the second air intake port is H5; wherein, H5<(H1 / 2+H2+H6 / 2).

[0010] Further, along the extending direction of the crankshaft, a distance between a central axis of the first cylinder body and a central axis of the first intake port is H7; wherein 0.05H1≤H7≤0.2H1.

[0011] Further, along the extending direction of the crankshaft, the distance between the central axis of the second cylinder body and the central axis of the second intake port is H8; wherein, 0.05H6≤H8≤0.2H6.

[0012] Furthermore, 0.2H2≤H4≤0.5H2; 0.2H2≤H3≤0.5H2.

[0013] Furthermore, the cylinder structure also includes a liquid distributor; the liquid outlet pipe of the liquid distributor is inserted into the air intake port.

[0014] A compressor comprises a cylinder structure, wherein the cylinder structure is the above-mentioned cylinder structure.

[0015] Beneficial effects: The cylinder structure of the present invention includes: a cylinder body, wherein the cylinder body has a compression chamber and an air intake port, one end of the air intake port is connected to the compression chamber, and the other end of the air intake port is connected to the outside of the cylinder body; a flange valve seat, wherein the flange valve seat is connected to the cylinder body, and an air outlet is arranged in the flange valve seat, and the air outlet is connected to the compression chamber; wherein the minimum distance between the axis of the air intake port and the flange valve seat is greater than the minimum distance between the axis of the air intake port and the end of the cylinder body away from the flange valve seat. The asymmetric cylinder air intake port structure can effectively optimize the size distribution of the impact on the upper and lower ends of the cylinder structure, can enlarge the cavity of the flange valve seat, further thin the valve seat, reduce the clearance volume and exhaust resistance, and improve the performance of the compressor; at the same time, in a small cylinder multi-cylinder structure, it can effectively reduce the deformation of the liquid distributor, improve the reliability of the liquid distributor, and solve the technical effect of low energy efficiency of the compressor in the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a schematic diagram of the cylinder structure of a single-cylinder compressor in the prior art; Figure 2 It is a schematic diagram of the cylinder structure of a double-cylinder compressor in the prior art; Figure 3 It is a structural schematic diagram of a double-cylinder compressor in the prior art; Figure 4 is a schematic diagram of a cylinder structure of a single-cylinder compressor used in an embodiment of the present invention; Figure 5 is a schematic diagram of a cylinder structure of a dual-cylinder compressor provided in an embodiment of the present invention; Figure 6 It is a schematic diagram of the dimensions of the cylinder structure of the dual-cylinder compressor provided in an embodiment of the present invention; Figure 7 is a cross-sectional view of a compressor provided by an embodiment of the present invention; Figure 8 yes Figure 7 A partial enlarged view of part I in FIG. Fig. 9 is a schematic structural diagram of a compressor provided by an embodiment of the present invention; Fig.10 yes Fig. 9 A partial enlarged view of part II in FIG. Fig.11 It is a deformation diagram of a liquid dispenser in the prior art; Fig.12 : is a stress diagram of a liquid dispenser in the prior art; Fig.13 : is a deformation diagram of the liquid dispenser of the present invention; Fig.14 : is a stress diagram of the dispenser of the present invention.

[0017] The above drawings include the following reference numerals: 1. Cylinder body; 101. First cylinder body; 102. Second cylinder body; 11. Compression chamber; 12. Air intake port; 121. First air intake port; 122. Second air intake port; 2. Flange valve seat; 201. First flange valve seat; 202. Second flange valve seat; 21. Air outlet; 3. Partition; 4. Crankshaft; 5. Liquid distributor; 51. Liquid outlet pipe; 6. Valve seat exhaust area. DETAILED DESCRIPTION

[0018] In order to enable those skilled in the art to better understand the cylinder structure of the present embodiment of the present application, the following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the cylinder structure of the present embodiment of the present application. Obviously, the described embodiment is only a part of the embodiment of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of this application.

[0019] See also Figures 1 to 14 According to an embodiment of the present invention, a cylinder structure is provided, comprising: a cylinder body 1, wherein the cylinder body 1 has a compression chamber 11 and an air intake port 12, wherein one end of the air intake port 12 is communicated with the compression chamber 11, and the other end of the air intake port 12 is communicated with the outside of the cylinder body 1; a flange valve seat 2, wherein the flange valve seat 2 is connected to the cylinder body 1, and an air outlet 21 is arranged in the flange valve seat 2, and the air outlet 21 is communicated with the compression chamber 11; wherein the minimum distance between the axis of the air intake port 12 and the flange valve seat 2 is greater than the minimum distance between the axis of the air intake port 12 and the end of the cylinder body 1 away from the flange valve seat 2.

[0020] Existing twin-cylinder compressors such as Figure 3 The compressor is composed of an upper cover, a lower cover, a housing assembly, a motor (not marked), a pump assembly, and a liquid distributor, wherein the pump assembly is composed of an upper flange, a lower flange, an upper cylinder, a partition, a lower cylinder, a roller (not marked), a vane (not marked), and a crankshaft. Existing single-cylinder compressors, such as Figure 1 As shown in the figure, compared with the double cylinder compressor, it has one less cylinder, roller, vane and partition. The existing single cylinder and double cylinder pump body suction port pressure diagram is as follows Figure 2 , the high-pressure and low-pressure areas in the pump cylinder are separated by the compressor vanes, such as Figure 7 Position, the compressor suction pressure is low pressure, the exhaust pressure is high pressure. The flow path and assembly diagram are as follows Figure 2, there is an upper flange structure on the upper side of the cylinder, the valve seat thickness is H9 and H10, H10>H9, the valve seat exhaust angle a, angle a is 30-60° to reduce exhaust resistance. The existing compressor efficiency improvement means often reduce the clearance volume and exhaust resistance of the exhaust high pressure area by reducing the valve seat thickness dimensions H3 and H4 to achieve efficiency improvement, but after the valve seat thickness is reduced, the impact of the valve seat from the suction port increases, the valve seat deformation will increase, and the valve seat reliability will deteriorate, resulting in the inability to improve the efficiency of the compressor.

[0021] The liquid distributor is composed of a curved pipe, a straight pipe, an upper cylinder, a lower cylinder, an air intake pipe, a middle partition, and a filter. The distance between the centers of the two curved pipes is limited by the center-to-center distance of the cylinder air intake port. When the center-to-center distance of the cylinder air intake port is different, the center-to-center distance of the liquid distributor curved pipe will be different, which will lead to the addition of new liquid distributors, resulting in an increase in the types of liquid distributors and poor universalization. The distance between the centers of the liquid distributor curved pipes should be as small as possible. When the center distance increases, the deformation and stress of the liquid distributor will increase, and the reliability of the liquid distributor will deteriorate.

[0022] By adopting the cylinder structure of this embodiment, the minimum distance between the axis of the air intake port 12 and the flange valve seat 2 is greater than the minimum distance between the axis of the air intake port 12 and the end of the cylinder body 1 away from the flange valve seat 2, thereby achieving an effect that the height distance from the air intake port 12 to the exhaust end of the cylinder body 1 is greater than half the cylinder height, forming an asymmetric cylinder air intake port structure, which can effectively optimize the distribution of the size of the impact on the upper and lower ends of the cylinder structure, and can enlarge the cavity of the flange valve seat 2, further thin the valve seat, reduce the clearance volume and exhaust resistance, and improve the performance of the compressor; at the same time, in a small cylinder body multi-cylinder structure, it can effectively reduce the deformation of the distributor, improve the reliability of the distributor, and solve the problem of low energy efficiency of the compressor in the prior art.

[0023] In the cylinder structure of this embodiment, see Figures 1 to 10The cylinder body 1 includes a first cylinder body 101 and a second cylinder body 102; the flange valve seat 2 includes a first flange valve seat 201 and a second flange valve seat 202; the first cylinder body 101 and the second cylinder body 102 are both located between the first flange valve seat 201 and the second flange valve seat 202; the first cylinder body 101 is connected to the first flange valve seat 201, and the second cylinder body 102 is connected to the second flange valve seat 202; the first cylinder body 101 is provided with a first compression chamber 11 and a first air intake port 121 connected to the first compression chamber 11; A second compression chamber 11 and a second air intake port 122 connected to the second compression chamber 11 are provided in the second cylinder body 102; wherein, the minimum distance between the first air intake port 121 and the first flange valve seat 201 is greater than the minimum distance between the first air intake port 121 and an end of the first cylinder body 101 away from the first flange valve seat 201; and the minimum distance between the second air intake port 122 and the second flange valve seat 202 is greater than the minimum distance between the second air intake port 122 and an end of the second cylinder body 102 away from the second flange valve seat 202.

[0024] By adopting the above-mentioned setting, when the cylinder structure is a double-cylinder, an asymmetric cylinder suction port structure is formed, which can effectively optimize the distribution of the impact on the upper and lower ends of the cylinder structure, and can enlarge the cavity of the flange valve seat 2, further thin the valve seat, reduce the clearance volume and exhaust resistance, and improve the performance of the compressor; at the same time, in a small cylinder body multi-cylinder structure, it can effectively reduce the deformation of the distributor and improve the reliability of the distributor.

[0025] In the cylinder structure of this embodiment, see Figure 6 The cylinder structure includes a partition plate 3, and the partition plate 3 is located between the first cylinder body 101 and the second cylinder body 102, so that the first cylinder body 101 and the second cylinder body 102 are spaced apart.

[0026] With the above arrangement, the partition plate 3 separates the upper and lower cylinder bodies, thereby strengthening the overall structure of the cylinder structure and making the cylinder structure more stable during air intake.

[0027] In the cylinder structure of this embodiment, see Fig. 9 The cylinder structure also includes a crankshaft 4, which passes through the cylinder body 1 and the flange valve seat 2; along the direction parallel to the axis of the crankshaft 4, the thickness of the partition 3 is H2, the thickness of the first cylinder body 101 is H1, the thickness of the second cylinder body 102 is H6, the minimum thickness of the valve seat exhaust area 6 in the first flange valve seat 201 is H3, and the minimum thickness of the valve seat exhaust area of ​​the second flange valve seat 202 is H4; wherein, H1>H2>H3, H6>H2>H4.

[0028] Specifically, H1 is the height of the upper cylinder, H2 is the height of the partition, H6 is the height of the lower cylinder, H3 is the minimum thickness of the exhaust area of ​​the upper flange valve seat, and H4 is the minimum thickness of the exhaust area of ​​the lower flange valve seat. The above settings can effectively reduce H3 and H4, reduce the clearance volume of the compressor exhaust high-pressure area and the exhaust resistance of the exhaust high-pressure area, improve the energy efficiency of the compressor, and at the same time obtain a high-reliability liquid distributor with a sufficiently low suction port center distance H5, and the space occupied by the liquid distributor is simultaneously reduced, effectively optimizing the system space utilization.

[0029] See also Figure 6 In the cylinder structure of this embodiment, the center distance between the first air intake port 121 and the second air intake port 122 is H5; wherein H5<(H1 / 2+H2+H6 / 2).

[0030] Specifically, H2 is the thickness of the partition, which cannot be too thick. If it is too thick, the weight of the pump body will increase. If it is too thin, the strength will not be enough and deformation will occur. H3 is the minimum thickness of the upper flange valve seat area. If it is too thin, it will be easily deformed. If it is too thick, it will increase the exhaust clearance volume of the compressor (the volume contained in the exhaust port, not involved in compression). H4 is the minimum thickness of the lower flange valve seat area. If it is too thin, it will be easily deformed. If it is too thick, it will increase the exhaust clearance volume of the compressor. In extreme cases, H4 should not be less than H3. If it is less than H3, abnormal wear will occur.

[0031] In the cylinder structure of this embodiment, see Figure 6 , along the extending direction of the crankshaft 4 , the distance between the central axis of the first cylinder body 101 and the central axis of the first intake port 121 is H7; wherein 0.05H1≤H7≤0.2H1.

[0032] See also Figure 6 In the cylinder structure of this embodiment, along the extension direction of the crankshaft 4, the distance between the central axis of the second cylinder body 102 and the central axis of the second intake port 122 is H8; wherein 0.05H6≤H8≤0.2H6.

[0033] Specifically, the H7 / H8 dimension specification can effectively reduce H9 / H10 and angle a to reduce the overall compressor exhaust clearance volume. And the strength of the parts meets the design requirements.

[0034] In the cylinder structure of this embodiment, see Figure 6 , 0.2H2≤H4≤0.5H2; 0.2H2≤H3≤0.5H2.

[0035] The above arrangement can ensure the strength of the structure while increasing the working efficiency of the cylinder structure.

[0036] In the cylinder structure of this embodiment, see Fig. 9The cylinder structure further includes a liquid distributor 5 ; a liquid outlet pipe 51 of the liquid distributor 5 is inserted into the air intake port 12 .

[0037] By adopting the above arrangement, a high-reliability dispenser with a universal air inlet center distance of H5 can be obtained, and the space occupied by the dispenser is simultaneously reduced, effectively optimizing the space utilization of the system.

[0038] The compressor of this embodiment includes a cylinder structure, and the cylinder structure is the above-mentioned cylinder structure.

[0039] The flange at the exhaust end of the cylinder is limited by the impact and cannot be further thinned, so the suction resistance and clearance volume cannot be reduced, and the energy efficiency of the compressor cannot be improved. With the above arrangement, the flange at the exhaust end of the cylinder can be further thinned, thereby improving the energy efficiency of the compressor.

[0040] In the cylinder structure of this embodiment, the air intake ports of multiple cylinders are all offset from the center of each cylinder (the deviation direction is close to the partition direction), see Figures 4 to 6 , H1>H2>H3, H6>H2>H4, H4≥H3, H5<(H1 / 2+H2+H6 / 2), H7=(0.05-0.2)H1, H8=(0.05-0.2)H6, H4=(0.2-0.5)H2, H3=(0.2-0.5)H2. This structure can effectively reduce H3 and H4, reduce the clearance volume and exhaust resistance in the high-pressure exhaust area of ​​the compressor, and improve the energy efficiency of the compressor. At the same time, a high-reliability distributor with a sufficiently low suction port center distance H5 can be obtained, and the space occupied by the distributor is simultaneously reduced, effectively optimizing the system space utilization.

[0041] The cylinder structure, compressor flow path and dimension diagram of this embodiment are shown in Figure 10 First, the compressor suction flow path is far away from the cylinder exhaust side (flange side), and the impact on the flange is small, so the valve seat size can be reduced to achieve energy efficiency improvement. The size changes: H9 size is reduced by 0.3mm, an overall reduction of 10-15%, H10 size is reduced by 2-4mm, an overall reduction of more than 30%, and the a angle is reduced to half of the original angle. The overall compressor exhaust resistance is reduced, and the clearance volume is reduced. According to this structure, when the cylinder height increases, the type of distributor is not increased, and the reliability of the distributor is improved.

[0042] Embodiment 1: The cylinder structure of this embodiment corresponds to the deformation of the liquid distributor, and the height difference H5 of the air intake pipe is changed from 29mm to 26mm. Theoretical simulation, the simulation diagram is as follows Figures 11 to 14 ,in Fig.11 and Fig.12 is the deformation diagram and stress diagram of the original dispenser, Fig.13 and Fig.14The deformation diagram and stress diagram of the liquid distributor corresponding to the cylinder structure of the new embodiment are shown. The maximum deformation is reduced by 15.6%, the maximum stress is reduced by 7.4%, the reliability of the liquid distributor is significantly improved, and the generalization requirements within the factory are met, increasing the space utilization of the system.

[0043] The valve seat size H9 was adjusted from 2.4 to 2.1, and the suction area size H10 was adjusted from 5.2 to 2.2. The compressor volumetric efficiency increased by 0.7%, the indicated efficiency increased by 0.5%, and the compressor energy efficiency increased by 1%.

[0044] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchangeable where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any of their variations are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device comprising a series of steps or units is not necessarily limited to those steps or units clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0045] Optionally, the specific examples in this embodiment may refer to the examples described in the above embodiments, and this embodiment will not be described in detail here.

[0046] The serial numbers of the above-mentioned embodiments of the present application are for description only and do not represent the advantages or disadvantages of the embodiments.

[0047] In the above embodiments of the present application, the description of each embodiment has its own emphasis. For parts that are not described in detail in a certain embodiment, please refer to the relevant description of other embodiments.

[0048] The above is only a preferred implementation of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present application. These improvements and modifications should also be regarded as the scope of protection of the present application.

Claims

1. A cylinder structure, characterized in that: include: A cylinder body (1), wherein the cylinder body (1) has a compression chamber (11) and an air intake port (12), one end of the air intake port (12) is connected to the compression chamber (11), and the other end of the air intake port (12) is connected to the outside of the cylinder body (1); A flange valve seat (2), the flange valve seat (2) being connected to the cylinder body (1), an air outlet (21) being provided in the flange valve seat (2), and the air outlet (21) being communicated with the compression chamber (11); The minimum distance between the axis of the air intake port (12) and the flange valve seat (2) is greater than the minimum distance between the axis of the air intake port (12) and an end of the cylinder body (1) away from the flange valve seat (2).

2. The cylinder structure according to claim 1, characterized in that: The cylinder body (1) comprises a first cylinder body (101) and a second cylinder body (102); the flange valve seat (2) comprises a first flange valve seat (201) and a second flange valve seat (202); the first cylinder body (101) and the second cylinder body (102) are both located between the first flange valve seat (201) and the second flange valve seat (202); the first cylinder body (101) is connected to the first flange valve seat (201), and the second cylinder body (102) is connected to the second flange valve seat (202); a first compression chamber (11) and a first air intake port (121) in communication with the first compression chamber (11) are provided in the first cylinder body (101); and a second compression chamber (11) and a second air intake port (122) in communication with the second compression chamber (11) are provided in the second cylinder body (102); The minimum distance between the first air intake port (121) and the first flange valve seat (201) is greater than the minimum distance between the first air intake port (121) and an end of the first cylinder body (101) away from the first flange valve seat (201); and the minimum distance between the second air intake port (122) and the second flange valve seat (202) is greater than the minimum distance between the second air intake port (122) and an end of the second cylinder body (102) away from the second flange valve seat (202).

3. The cylinder structure according to claim 2, characterized in that: The cylinder structure comprises a partition plate (3), wherein the partition plate (3) is located between the first cylinder body (101) and the second cylinder body (102), so that the first cylinder body (101) and the second cylinder body (102) are arranged at a distance.

4. The cylinder structure according to claim 3, characterized in that: The cylinder structure further comprises a crankshaft (4), wherein the crankshaft (4) passes through the cylinder body (1) and the flange valve seat (2); along a direction parallel to the axis of the crankshaft (4), the thickness of the partition plate (3) is H2, the thickness of the first cylinder body (101) is H1, the thickness of the second cylinder body (102) is H6, the minimum thickness of the valve seat exhaust area (6) in the first flange valve seat (201) is H3, and the minimum thickness of the valve seat exhaust area of ​​the second flange valve seat (202) is H4; wherein H1>H2>H3, and H6>H2>H4.

5. The cylinder structure according to claim 4, characterized in that: The center distance between the first air intake port (121) and the second air intake port (122) is H5; wherein H5<(H1 / 2+H2+H6 / 2).

6. The cylinder structure according to claim 4, characterized in that: Along the extending direction of the crankshaft (4), the distance between the central axis of the first cylinder body (101) and the central axis of the first air intake port (121) is H7; wherein 0.05H1≤H7≤0.2H1.

7. The cylinder structure according to claim 4, characterized in that: Along the extending direction of the crankshaft (4), the distance between the central axis of the second cylinder body (102) and the central axis of the second air intake port (122) is H8; wherein 0.05H6≤H8≤0.2H6.

8. The cylinder structure according to claim 4, characterized in that: 0.2H2≤H4≤0.5H2; 0.2H2≤H3≤0.5H2.

9. The cylinder structure according to any one of claims 1 to 8, characterized in that: The cylinder structure further comprises a liquid distributor (5); a liquid outlet pipe (51) of the liquid distributor (5) is inserted into the air intake port (12).

10. A compressor, comprising a cylinder structure, characterized in that: The cylinder structure is the cylinder structure according to any one of claims 1 to 9.

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