Air cylinder structure and compressor

Abstract

The utility model 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; 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 air cylinder structure solves the technical problem that in the prior art, a compressor is low in energy efficiency.

Description

TECHNICAL FIELD

[0001] The utility model relates to a compressor technical field, concretely relates to a cylinder structure and compressor. BACKGROUND

[0002] Compressor energy efficiency and cost are the direction that customers pay most attention to, with the promotion of prior art, small cylinder structure is often used to replace big cylinder structure compressor to realize cost optimization. Meanwhile, the cylinder structure of the prior art embodiment, the center of the intake pipe and the cylinder center plane are at the same height, thereby bringing the following problems:

[0003] ①In the existing compressor structure, when the suction center distance is in the middle, the suction flow path uniformly impacts the structure of the upper and lower ends of the cylinder, limited by the impact size received by the exhaust end, the exhaust end flange valve seat thickness cannot be thinned, so the suction resistance and clearance volume cannot be reduced, and finally the compressor energy efficiency cannot be improved. ②Small cylinder body is limited by the cylinder body outer diameter size, commonly uses the way of increasing cylinder height to increase displacement, in the multi-cylinder structure, the center distance between cylinders increases, cannot adapt to the distributor of big cylinder structure, increases the type of distributor, and the distance between the suction pipes increases the structural strength, also increases the distributor space, is not conducive to compact structure.

[0004] Therefore, the prior art needs to be further developed. UTILITY MODEL CONTENTS

[0005] The utility model aims at overcoming the above technical deficiencies, providing a cylinder structure and compressor to solve the technical problem of low energy efficiency of the compressor in the related art.

[0006] To achieve the above technical purpose, the utility model adopts the following technical cylinder structure of the embodiment: a cylinder structure is provided, which comprises:

[0007] A cylinder body has a compression chamber and a suction port inside, one end of the suction port is communicated with the compression chamber, and the other end of the suction port is communicated to the outside of the cylinder body;

[0008] A flange valve seat is connected with the cylinder body, an air outlet is arranged in the flange valve seat, and the air outlet is communicated with the compression chamber;

[0009] Wherein, the minimum distance between the axis of the suction port and the flange valve seat is greater than the minimum distance between the axis of the suction port and one end of the cylinder body away from the flange valve seat.

[0010] Further, the cylinder body comprises a first cylinder body and a second cylinder body; the flange valve seat comprises a first flange valve seat and a second flange valve seat; the first cylinder body and the second cylinder body are located between the first flange valve seat and the second flange valve seat; the first cylinder body is connected with the first flange valve seat, and the second cylinder body is connected with the second flange valve seat; the first cylinder body is provided with a first compression cavity and a first air inlet communicating with the first compression cavity; the second cylinder body is provided with a second compression cavity and a second air inlet communicating with the second compression cavity.

[0011] Wherein, the minimum distance between the first air inlet and the first flange valve seat is less than the minimum distance between the first air inlet and one end of the first cylinder body away from the first flange valve seat; the minimum distance between the first air inlet and the first flange valve seat is greater than the minimum distance between the first air inlet and one end of the first cylinder body away from the first flange valve seat; the minimum distance between the second air inlet and the second flange valve seat is greater than the minimum distance between the second air inlet and one end of the second cylinder body away from the second flange valve seat.

[0012] Further, the cylinder structure comprises a partition plate, which is located between the first cylinder body and the second cylinder body to separate the first cylinder body and the second cylinder body.

[0013] Further, the cylinder structure further comprises a crankshaft, which passes through the cylinder body and the flange valve seat; in the direction parallel to the axis of the crankshaft, the thickness of the partition plate 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.

[0014] Further, the center distance between the first air inlet and the second air inlet is H5; wherein, H5<(H1 / 2+H2+H6 / 2).

[0015] Further, in the extension direction of the crankshaft, the distance between the central axis of the first cylinder body and the central axis of the first air inlet is H7; wherein, 0.05H1≤H7≤0.2H1.

[0016] Further, in the extension direction of the crankshaft, the distance between the central axis of the second cylinder body and the central axis of the second air inlet is H8; wherein, 0.05H6≤H8≤0.2H6.

[0017] Further, 0.2H2≤H4≤0.5H2; 0.2H2≤H3≤0.5H2.

[0018] Further, the cylinder structure further comprises a distributor; a liquid outlet pipe of the distributor is inserted into the suction port.

[0019] A compressor comprises a cylinder structure, which is the cylinder structure described above.

[0020] Advantages:

[0021] The cylinder structure comprises: a cylinder body, the cylinder body has a compression cavity and a suction port, one end of the suction port is communicated with the compression cavity, and the other end of the suction port is communicated to the outside of the cylinder body; a flange valve seat, the flange valve seat is connected with the cylinder body, an air outlet is arranged in the flange valve seat, and the air outlet is communicated with the compression cavity; wherein the minimum distance between the axis of the suction port and the flange valve seat is greater than the minimum distance between the axis of the suction port and one end of the cylinder body away from the flange valve seat. The asymmetric cylinder suction port structure can effectively optimize the size distribution of impacts 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; meanwhile, in a small cylinder body multi-cylinder structure, the deformation of the distributor can be effectively reduced, the reliability of the distributor is improved, and the technical effect that the compressor in the prior art has low energy efficiency is solved. BRIEF DESCRIPTION OF DRAWINGS

[0022] Figure 1 is a schematic view of a cylinder structure of a single-cylinder compressor in the prior art;

[0023] Figure 2 is a schematic view of a cylinder structure of a double-cylinder compressor in the prior art;

[0024] Figure 3 is a schematic view of a double-cylinder compressor in the prior art;

[0025] Figure 4 is a schematic view of a cylinder structure of a single-cylinder compressor adopted in an embodiment of the utility model;

[0026] Figure 5 is a schematic view of a cylinder structure of a double-cylinder compressor provided in an embodiment of the utility model;

[0027] Figure 6 is a size schematic view of a cylinder structure of a double-cylinder compressor provided in an embodiment of the utility model;

[0028] Figure 7 is a sectional view of a compressor provided in an embodiment of the utility model;

[0029] Figure 8 is Figure 7 is a local enlarged view of I part in the figure;

[0030] Figure 9 is a structural schematic diagram of a compressor provided by the embodiment of the present application;

[0031] Figure 10 is Figure 9 is a partial enlarged view of the II part in

[0032] Figure 11 is a deformation diagram of a distributor in the prior art;

[0033] Figure 12 is a stress diagram of a distributor in the prior art;

[0034] Figure 13 is a deformation diagram of a distributor of the present application;

[0035] Figure 14 is a stress diagram of a distributor of the present application.

[0036] Among them, the above drawings include the following reference signs:

[0037] 1, cylinder; 101, first cylinder; 102, second cylinder; 11, compression chamber; 12, suction port; 121, first suction port; 122, second suction port; 2, flange valve seat; 201, first flange valve seat; 202, second flange valve seat; 21, gas outlet; 3, partition plate; 4, crankshaft; 5, distributor; 51, liquid outlet pipe; 6, valve seat exhaust area. DETAILED DESCRIPTION

[0038] In order to enable the personnel in the technical field to better understand the cylinder structure of the present application, the technical cylinder structure of the present application will be described clearly and completely below in combination with the drawings in the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, not all. Based on the embodiments in the present application, all other embodiments obtained by the ordinary skilled in the art without creative labor should belong to the scope of protection of the present application.

[0039] Referring to Figures 1 to 14 According to the embodiment of the present application, a cylinder structure is provided, comprising: a cylinder 1, the cylinder 1 has a compression chamber 11 and a suction port 12 inside, one end of the suction port 12 is communicated with the compression chamber 11, and the other end of the suction port 12 is communicated to the outside of the cylinder 1; a flange valve seat 2, the flange valve seat 2 is connected with the cylinder 1, the flange valve seat 2 is provided with a gas outlet 21 inside, and the gas outlet 21 is communicated with the compression chamber 11; wherein the minimum distance between the axis of the suction port 12 and the flange valve seat 2 is greater than the minimum distance between the axis of the suction port 12 and the end of the cylinder 1 away from the flange valve seat 2.

[0040] The existing double-cylinder compressor, as shown in Figure 3 , is composed of an upper cover, a lower cover, a shell assembly, a motor (not shown), a pump body assembly, and a distributor. The pump body assembly is composed of an upper flange, a lower flange, an upper cylinder, a partition plate, a lower cylinder, a roller (not shown), a sliding vane (not shown), and a crankshaft. The existing single-cylinder compressor, as shown in Figure 1 , has one less cylinder, roller, sliding vane, and partition plate compared to the double-cylinder compressor. The existing single-cylinder and double-cylinder pump body suction port pressure diagram is as shown in Figure 2 . The high-pressure and low-pressure areas in the pump body cylinder are divided by the compressor sliding vane, as shown in Figure 7 . The compressor suction pressure is low, and the exhaust pressure is high. The flow path and assembly diagram is as shown in Figure 2 . The upper side of the cylinder has an upper flange structure, valve seat thickness H9 and H10, H10 > H9, valve seat exhaust angle a, and a angle of 30-60° to reduce exhaust resistance. The existing compressor efficiency improvement method often reduces the valve seat thickness dimensions H3 and H4 to reduce the clearance volume of the exhaust high-pressure area and the exhaust resistance of the exhaust high-pressure area to achieve efficiency improvement. However, after reducing the valve seat thickness, the valve seat impact from the suction port increases, the valve seat deformation increases, and the valve seat reliability deteriorates, which prevents the compressor from improving efficiency.

[0041] The distributor is composed of an elbow pipe, a straight pipe, an upper cylinder, a lower cylinder, a suction pipe, an intermediate partition plate, and a filter screen. The distance between the centers of the two elbow pipes is limited by the center-to-center distance of the cylinder suction port. When the center-to-center distance of the cylinder suction port is different, the center distance of the distributor elbow pipe will also be different, resulting in the addition of a distributor, causing an increase in the types of distributors and poor generalization. The smaller the distance between the centers of the distributor elbow pipes, the better. When the center distance increases, the distributor deformation and stress increase, and the distributor reliability deteriorates.

[0042] The cylinder structure of the present embodiment has a minimum distance between the axis of the suction port 12 and the flange valve seat 2 greater than the minimum distance between the axis of the suction port 12 and the end of the cylinder body 1 away from the flange valve seat 2, thereby achieving an effect of the height distance from the suction port 12 to the exhaust end of the cylinder body 1 greater than half the height of the cylinder, forming an asymmetric cylinder suction port structure that can effectively optimize the size distribution of the impact on the upper and lower ends of the cylinder structure, increase 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 with multiple cylinder structures, the distributor deformation can be effectively reduced, and the distributor reliability can be improved, solving the problem of low energy efficiency of the compressor in the prior art.

[0043] In the cylinder structure of the present embodiment, as shown in Figures 1 to 10The 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 located between the first flange valve seat 201 and the second flange valve seat 202; the first cylinder body 101 is connected with the first flange valve seat 201, and the second cylinder body 102 is connected with the second flange valve seat 202; the first cylinder body 101 is provided with a first compression cavity 11 and a first suction port 121 communicated with the first compression cavity 11; the second cylinder body 102 is provided with a second compression cavity 11 and a second suction port 122 communicated with the second compression cavity 11; wherein the minimum distance between the first suction port 121 and the first flange valve seat 201 is less than the minimum distance between the first suction port 121 and one end of the first cylinder body 101 away from the first flange valve seat 201; the minimum distance between the first suction port 121 and the first flange valve seat 201 is greater than the minimum distance between the first suction port 121 and one end of the first cylinder body 101 away from the first flange valve seat 201; and the minimum distance between the second suction port 122 and the second flange valve seat 202 is greater than the minimum distance between the second suction port 122 and one end of the second cylinder body 102 away from the second flange valve seat 202.

[0044] With the above arrangement, when the cylinder structure is double-cylinder, an asymmetric cylinder suction port structure is formed, which can effectively optimize the size distribution of the impact on the upper and lower ends of the cylinder structure, can increase 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 the small cylinder multi-cylinder structure, the deformation of the distributor can be effectively reduced, and the reliability of the distributor can be improved.

[0045] In the cylinder structure of the embodiment, referring to Figure 6 The cylinder structure comprises a partition plate 3 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 in a spaced manner.

[0046] 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 suction.

[0047] In the cylinder structure of the embodiment, referring to Figure 9The cylinder structure further comprises a crankshaft 4 penetrating through the cylinder block 1 and the flange valve seat 2; the thickness of the partition plate 3 is H2, the thickness of the first cylinder block 101 is H1, the thickness of the second cylinder block 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.

[0048] Specifically, H1 is the upper cylinder height, H2 is the partition plate height, H6 is the lower cylinder height, H3 is the minimum thickness of the upper flange valve seat exhaust area, and H4 is the minimum thickness of the lower flange valve seat exhaust area. With the above arrangement, H3 and H4 can be effectively reduced, the clearance volume of the compressor exhaust high-pressure area and the exhaust resistance of the exhaust high-pressure area can be reduced, the compressor efficiency can be improved, and a high-reliability distributor with a low enough center distance H5 of the suction ports can be obtained, the space occupied by the distributor is simultaneously reduced, and the system space utilization rate is effectively optimized.

[0049] Referring to Figure 6 In the cylinder structure of the embodiment, the center distance between the first suction port 121 and the second suction port 122 is H5; wherein H5<(H1 / 2+H2+H6 / 2).

[0050] Specifically, H2 is the partition plate thickness, which cannot be too thick, otherwise the pump body weight will be increased, and 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, which is easy to deform if it is too thin, and the compressor exhaust clearance volume (contained in the exhaust port volume and not involved in compression) will be increased if it is too thick. H4 is the minimum thickness of the lower flange valve seat area, which is easy to deform if it is too thin, and the compressor exhaust clearance volume will be increased if it is too thick. In the extreme case, H4 is not less than H3, otherwise abnormal wear will occur.

[0051] In the cylinder structure of the embodiment, referring to Figure 6 , along the extension direction of the crankshaft 4, the distance between the central axis of the first cylinder block 101 and the central axis of the first suction port 121 is H7; wherein 0.05H1≤H7≤0.2H1.

[0052] Referring to Figure 6 In the cylinder structure of the embodiment, along the extension direction of the crankshaft 4, the distance between the central axis of the second cylinder block 102 and the central axis of the second suction port 122 is H8; wherein 0.05H6≤H8≤0.2H6.

[0053] Specifically, H7 / H8 is set to a size specification, which can effectively reduce H9 / H10 and the angle a to reduce the compressor exhaust clearance volume as a whole. Moreover, the strength of the parts meets the design requirements.

[0054] In the cylinder structure of the embodiment, referring to Figure 6 0.2H2≤H4≤0.5H2; 0.2H2≤H3≤0.5H2.

[0055] With the above arrangement, the strength of the structure can be ensured while the working efficiency of the cylinder structure is increased.

[0056] In the cylinder structure of the embodiment, referring to Figure 9 The cylinder structure further comprises a distributor 5; and a liquid outlet pipe 51 of the distributor 5 is arranged in the suction port 12.

[0057] With the above arrangement, a high-reliability distributor with a general suction port center distance H5 can be obtained, and the space occupied by the distributor is simultaneously reduced, thereby effectively optimizing the space utilization rate of the system.

[0058] The compressor of the embodiment comprises the cylinder structure described above.

[0059] The flange at the exhaust end of the cylinder is limited by the impact received and cannot be further thinned in design, so that the suction resistance and the clearance volume cannot be reduced, and finally 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.

[0060] In the cylinder structure of the embodiment, the suction ports of the plurality of cylinders are all offset from the respective centers of the cylinders (the offset direction is the direction close to the partition plate), referring to 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 in the high-pressure exhaust area of the compressor and the exhaust resistance in the high-pressure exhaust area, improve the energy efficiency of the compressor, and at the same time, a high-reliability distributor with a low enough suction port center distance H5 can be obtained, the space occupied by the distributor is simultaneously reduced, and the space utilization rate of the system is effectively optimized.

[0061] In the cylinder structure of the embodiment, referring to Figure 10 One, the suction flow path of the compressor is far away from the exhaust side of the cylinder (the flange side), and the impact on the flange is small, so that the size of the valve seat can be reduced to improve the energy efficiency, and the size changes: the size of H9 is reduced by 0.3 mm, the overall size is reduced by 10-15%, the size of H10 is reduced by 2-4 mm, the overall size is reduced by more than 30%, and the a angle can be reduced to half of the original angle, the overall exhaust resistance of the compressor is reduced, the clearance volume is reduced, and according to the structure, the type of the distributor is not increased under the condition of increasing the cylinder height, and the reliability of the distributor is improved.

[0062] Embodiment one:

[0063] The cylinder structure of the embodiment corresponds to the distributor deformation, the height difference H5 of the suction pipe is changed from 29mm to 26mm, the theoretical simulation is simulated, and the simulation diagram is as follows Figures 11 to 14 , wherein Figure 11 and Figure 12 are the original distributor deformation diagram and stress diagram, Figure 13 and Figure 14 are the deformation diagram and stress diagram of the new cylinder structure of the embodiment corresponding to the distributor, the maximum deformation is reduced by 15.6%, the maximum stress is reduced by 7.4%, the reliability of the distributor is obviously improved, and the general requirements of the factory are met at the same time, and the system space utilization rate is increased.

[0064]

[0065] The valve seat size H9 is adjusted from 2.4 to 2.1, the suction area size H10 is adjusted from 5.2 to 2.2, the volumetric efficiency of the compressor is improved by 0.7%, the indicated efficiency is improved by 0.5%, and the energy efficiency of the compressor is improved by 1%.

[0066]

[0067] It should be noted that the terms "first", "second", and the like in the specification and claims of the application and the above-mentioned drawings are used to distinguish similar objects, and do not necessarily describe a specific order or sequence. It should be understood that the data thus used can be interchanged under appropriate circumstances, so that the embodiments of the application described herein can be implemented in an order other than that illustrated or described herein. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion, for example, a process, method, system, product or device including a series of steps or units does not necessarily limit to those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0068] Alternatively, the specific examples in the embodiment can refer to the examples described in the above embodiments, and the embodiment will not be described here.

[0069] The serial numbers of the above embodiments of the application are only for description, and do not represent the advantages and disadvantages of the embodiments.

[0070] In the above embodiments of the application, the description of each embodiment has its own emphasis, and the parts not described in detail in a certain embodiment can refer to the related description of other embodiments.

[0071] The above merely describes the preferred embodiments of the present application, and it should be pointed out that, for those skilled in the art, some improvements and refinements can be made without departing from the principles of the present application, and these improvements and refinements should also be considered as the protection scope of the present application.

Claims

1. A cylinder structure characterized by comprising: The cylinder (1) has a compression chamber (11) and an air inlet (12) inside, one end of the air inlet (12) communicates with the compression chamber (11), and the other end of the air inlet (12) communicates to the outside of the cylinder (1); The flange valve seat (2) is connected with the cylinder (1), and the flange valve seat (2) is provided with an air outlet (21) inside, and the air outlet (21) communicates with the compression chamber (11); The minimum distance between the axis of the air inlet (12) and the flange valve seat (2) is greater than the minimum distance between the axis of the air inlet (12) and the end of the cylinder (1) away from the flange valve seat (2). The cylinder (1) includes a first cylinder (101) and a second cylinder (102); the flange valve seat (2) includes a first flange valve seat (201) and a second flange valve seat (202); the first cylinder (101) and the second cylinder (102) are located between the first flange valve seat (201) and the second flange valve seat (202); the first cylinder (101) is connected with the first flange valve seat (201), and the second cylinder (102) is connected with the second flange valve seat (202); the first cylinder (101) is provided with a first compression chamber (11) and a first air inlet (121) communicating with the first compression chamber (11); the second cylinder (102) is provided with a second compression chamber (11) and a second air inlet (122) communicating with the second compression chamber (11); 2. The cylinder structure according to claim 1, characterized by The minimum distance between the first air inlet (121) and the first flange valve seat (201) is less than the minimum distance between the first air inlet (121) and the end of the first cylinder (101) away from the first flange valve seat (201); the minimum distance between the first air inlet (121) and the first flange valve seat (201) is greater than the minimum distance between the first air inlet (121) and the end of the first cylinder (101) away from the first flange valve seat (201); the minimum distance between the second air inlet (122) and the second flange valve seat (202) is greater than the minimum distance between the second air inlet (122) and the end of the second cylinder (102) away from the second flange valve seat (202). The cylinder structure includes a partition plate (3) located between the first cylinder (101) and the second cylinder (102) to separate the first cylinder (101) and the second cylinder (102).

3. The cylinder structure according to claim 2, characterized in that ​ 4. The cylinder structure according to claim 3, characterized in that The cylinder structure further comprises a crankshaft (4) penetrating through the cylinder block (1) and the flange valve seat (2); the thickness of the partition plate (3) is H2, the thickness of the first cylinder block (101) is H1, the thickness of the second cylinder block (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.

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

6. The cylinder structure according to claim 4, characterized by The distance between the central axis of the first cylinder block (101) and the central axis of the first air inlet (121) in the extension direction of the crankshaft (4) is H7; wherein 0.05H1≤H7≤0.2H1.

7. The cylinder structure according to claim 4, characterized by The distance between the central axis of the second cylinder block (102) and the central axis of the second air inlet (122) in the extension direction of the crankshaft (4) is H8; wherein 0.05H6≤H8≤0.2H6.

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

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

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

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