Compressor cylinder and rotor compressor

Abstract

The utility model provides a compressor air cylinder and a rotor compressor, the compressor air cylinder is provided with a main cavity, and the main cavity penetrates through the compressor air cylinder along the axial direction of the compressor air cylinder; the air suction holes and the exhaust holes communicate with the main cavity, and the air suction holes and the exhaust holes are formed in the circumferential direction of the compressor air cylinder at intervals; the sliding piece groove is formed between the air suction hole and the exhaust hole in the circumferential direction of the compressor air cylinder; the spring hole and the main cavity are arranged at an interval, and the spring hole is communicated with the slip sheet groove; the minimum distance d between the spring hole and the air suction hole is larger than or equal to 1.0 mm and smaller than or equal to 1.7 mm. The compressor cylinder solves the technical problem that the structural reliability and the performance of a compressor are difficult to consider in the prior art.

Description

TECHNICAL FIELD

[0001] The utility model relates to the compressor design field, specifically, a kind of compressor cylinder and rotor compressor. BACKGROUND

[0002] Compressor is important component in heat pump equipment such as air conditioner, and the quality of compressor will also largely determine the life and energy efficiency of heat pump equipment.

[0003] In the related art, when designing the compressor, the distance between the suction hole and the sliding vane groove is often designed, but this design method does not comprehensively consider the factors, and the compressor designed in this way may have poor structural reliability and / or poor operating performance in actual use, making it difficult to balance both, resulting in short service life and low energy efficiency.

[0004] Therefore, there is a technical problem in the related art that it is difficult to balance the structural reliability and performance of the compressor, and currently there is no effective solution to this technical problem. SUMMARY

[0005] The main purpose of the utility model is to provide a kind of compressor cylinder and rotor compressor, to solve the technical problem that it is difficult to balance the structural reliability and performance of the compressor in the related art.

[0006] To achieve the above purpose, according to one aspect of the utility model, a compressor cylinder is provided, which is provided with: a main cavity, the main cavity is arranged through the compressor cylinder along the axial direction of the compressor cylinder; a suction hole and an exhaust hole, the suction hole and the exhaust hole are both communicated with the main cavity, and the suction hole and the exhaust hole are arranged at intervals along the circumferential direction of the compressor cylinder; a sliding vane groove, along the circumferential direction of the compressor cylinder, the sliding vane groove is arranged between the suction hole and the exhaust hole; a spring hole, the spring hole is arranged at intervals with the main cavity, and the spring hole is communicated with the sliding vane groove; the minimum distance d between the spring hole and the suction hole satisfies: 1.0mm≤d≤1.7mm.

[0007] Further, the compressor cylinder is formed by powder metallurgy process, and along the circumferential direction of the compressor cylinder, the width of the sliding vane groove is 2.8mm.

[0008] Further, the ratio of the diameter of the spring hole to the inner diameter of the main cavity is in the range of 0.186 to 0.244.

[0009] Further, the diameter of the spring hole is in the range of Φ8mm to Φ9.5mm, and the inner diameter of the main cavity is in the range of Φ39mm to Φ43mm.

[0010] Further, the suction angle θ of the compressor cylinder is in the range of 21°≤θ≤25°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole.

[0011] Further, the suction hole has a hole diameter of 12mm, the spring hole has a hole diameter of 8mm, and the suction angle θ of the compressor cylinder is in the range of 21.5°≤θ≤23°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole.

[0012] Further, the suction hole has a hole diameter of 12mm, the spring hole has a hole diameter of 8.5mm, and the suction angle θ of the compressor cylinder is in the range of 22°≤θ≤23.5°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole.

[0013] Further, the suction hole has a hole diameter of 12mm, the spring hole has a hole diameter of 9mm, and the suction angle θ of the compressor cylinder is in the range of 22.5°≤θ≤24°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole.

[0014] Further, the suction hole has a hole diameter of 12mm, the spring hole has a hole diameter of 9.5mm, and the suction angle θ of the compressor cylinder is in the range of 23°≤θ≤24.6°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole.

[0015] According to another aspect of the present application, a rotor compressor is provided, which comprises the compressor cylinder as described above.

[0016] The compressor cylinder of the embodiment of the utility model is provided with: a main cavity, the main cavity is arranged along the axial direction of the compressor cylinder and penetrates the compressor cylinder; a suction hole and an exhaust hole, the suction hole and the exhaust hole are both communicated with the main cavity, and the suction hole and the exhaust hole are arranged at intervals along the circumferential direction of the compressor cylinder; a sliding vane groove, the sliding vane groove is arranged between the suction hole and the exhaust hole along the circumferential direction of the compressor cylinder; a spring hole, the spring hole is arranged at intervals with the main cavity, and the spring hole is communicated with the sliding vane groove; and the minimum distance d between the spring hole and the suction hole satisfies 1.0mm <= d <= 1.7mm. Since the spring hole is communicated with the sliding vane groove, and the width of the spring hole along the circumferential direction of the compressor cylinder is large, the spring hole will affect the relative position arrangement between the sliding vane groove and the suction hole, in the related art, only the distance between the sliding vane groove and the suction hole is considered when the compressor cylinder is designed, and the influence of the spring hole on the arrangement between the two is not considered, which leads to unreasonable parameter design, and the designed compressor is difficult to meet the requirements of structural reliability and high energy efficiency. The compressor cylinder with the above structure is designed, the minimum distance between the spring hole and the suction hole is optimized, and the minimum distance d between the two satisfies 1.0mm <= d <= 1.7mm. After the size parameter is designed, the situation that the distance between the spring hole and the suction hole is too small to cause material deformation or rupture between the two can be avoided, and the situation that the distance between the spring hole and the suction hole is too large to cause the suction hole to be too far away from the sliding vane groove, thereby reducing performance can also be avoided, and the structural reliability and performance of the compressor can be well balanced. BRIEF DESCRIPTION OF DRAWINGS

[0017] The drawings accompanying the specification of this application form a part thereof, serve to provide further understanding of the application, and together with the description of the application explain the application. In the drawings:

[0018] Figure 1 It is a structural schematic view of the embodiment of the compressor cylinder of the utility model;

[0019] Figure 2 It is a schematic view of the embodiment of the compressor cylinder of the utility model and related structure after assembly;

[0020] Figure 3 It is a structural schematic view of the embodiment of the compressor of the utility model;

[0021] Figure 4 It is a sectional view of the embodiment of the compressor of the utility model;

[0022] Figure 5 It is a schematic view of COP when the embodiment of the compressor of the utility model adopts different wall thickness (the minimum distance d between the spring hole and the suction hole).

[0023] Wherein, the above-mentioned drawings include the following reference signs:

[0024] 1, main cavity; 2, suction hole; 3, exhaust hole; 4, sliding vane groove; 5, spring hole; 10, compressor cylinder; 20, crankshaft; 30, piston; 40, sliding vane; 50, spring; 60, upper bearing; 70, lower bearing; 80, muffler. DETAILED DESCRIPTION

[0025] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0026] Please refer to Figure 1 In order to achieve the above-mentioned purpose, the embodiment of the present application provides a compressor cylinder, which is provided with: a main cavity 1, the main cavity 1 is arranged through the compressor cylinder along the axial direction of the compressor cylinder; a suction hole 2 and an exhaust hole 3, the suction hole 2 and the exhaust hole 3 are both communicated with the main cavity 1, and the suction hole 2 and the exhaust hole 3 are arranged at intervals along the circumferential direction of the compressor cylinder; a sliding vane groove 4, the sliding vane groove 4 is arranged between the suction hole 2 and the exhaust hole 3 along the circumferential direction of the compressor cylinder; a spring hole 5, the spring hole 5 is arranged at intervals with the main cavity 1, and the spring hole 5 is communicated with the sliding vane groove 4; and the minimum distance d between the spring hole 5 and the suction hole 2 satisfies: 1.0mm≤d≤1.7mm.

[0027] Since the spring hole 5 is communicated with the sliding vane groove 4, and the width of the hole diameter of the spring hole 5 along the circumferential direction of the compressor cylinder is large, the spring hole 5 will affect the relative position arrangement between the sliding vane groove 4 and the suction hole 2. In the related art, only the distance between the sliding vane groove 4 and the suction hole 2 is considered in the design of the compressor cylinder, and the influence of the spring hole 5 on the arrangement between the two is not considered, which leads to unreasonable parameter design, and the designed compressor is difficult to meet the requirements of structural reliability and high energy efficiency. The compressor cylinder with the above-mentioned structure design optimizes the minimum distance between the spring hole 5 and the suction hole 2, so that the minimum distance d between the two satisfies: 1.0mm≤d≤1.7mm. After the size parameter design, the situation that the distance between the spring hole 5 and the suction hole 2 is too small to cause material deformation or rupture between the two can be avoided, and the situation that the distance between the spring hole 5 and the suction hole 2 is too large to cause the suction hole 2 to be too far away from the sliding vane groove 4, thereby causing performance reduction, can also be avoided, so that the structural reliability and performance of the compressor can be well balanced.

[0028] As mentioned above, if the distance between the spring hole 5 and the suction hole 2 is too small, the material between the spring hole 5 and the suction hole 2 will be deformed or broken, and in particular, such deformation or breaking can occur in various cases, for example, due to the small distance between the spring hole 5 and the suction hole 2, the structural strength of the nearby position will be reduced, when the suction hole 2 and the connecting pipe are in interference fit, the extrusion force between the two can cause deformation or even breaking at the weak position; for example, when the compressor is running, the high pressure inside can also cause deformation or breaking at the weak position; for example, when the spring hole and the suction hole of the compressor cylinder are processed, due to the weak structure between the spring hole 5 and the suction hole 2, the processing process can cause the situation of breaking.

[0029] If the distance between the spring hole 5 and the suction hole 2 is too large, the suction hole 2 will be farther away from the vane groove 4, and when the piston of the compressor rotates in the main cavity 1, the refrigerant sucked into the main cavity 1 in the last cycle will flow back to the suction pipe from the suction hole 2, causing the suction volume to decrease, thereby reducing the energy efficiency. The closer the suction hole 2 is to the vane groove 4, the less refrigerant will flow back. However, the closer the suction hole 2 is to the vane groove 4, the smaller the distance between the spring hole 5 and the suction hole 2, which is not conducive to the strength of the structure between them. The embodiments of the present application design the minimum distance d between the spring hole 5 and the suction hole 2 to be 1.0mm≤d≤1.7mm, which can well avoid the occurrence of the above two defects, and balance the structural reliability and performance of the compressor, and ensure that the heat pump equipment has a high service life and high energy efficiency.

[0030] In order to better illustrate the operation process of the compressor, as Figures 2 to 4 When the above compressor cylinder is assembled into a compressor, the crankshaft 20 and the piston 30 are installed in the main cavity 1 of the compressor cylinder 10, the piston 30 is sleeved on the outside of the crankshaft 20, the vane 40 is installed in the vane groove 4, and the spring 50 is installed in the spring hole 5. The vane 40 is in contact with the surface of the piston 30 under the thrust of the spring 50, and the vane 40 and the piston 30 divide the main cavity 1 in the compressor cylinder 10 into suction and exhaust cavities. When the piston 30 rotates, the volume of the suction and exhaust cavities will change, thereby sucking the refrigerant from the suction hole 2, compressing it, and then discharging it through the exhaust hole 3.

[0031] In a preferred embodiment, the compressor cylinder is processed by a powder metallurgy process, and the width of the vane groove 4 along the circumference of the compressor cylinder is 2.8mm.

[0032] In the embodiment, the compressor cylinder is made of powder metallurgy process, and the width of the sliding vane groove 4 is designed to be 2.8 mm. In the prior art, the width of the sliding vane groove 4 of the compressor cylinder made of powder metallurgy process is generally large. In the embodiment, the width of the sliding vane groove 4 is designed to be 2.8 mm, which is beneficial to reduce the friction resistance of the sliding vane in the sliding vane groove 4, thereby improving the energy efficiency of the compressor. In combination with the design of the minimum distance between the spring hole 5 and the suction hole 2, the energy efficiency of the compressor can be further improved.

[0033] Specifically, the ratio of the hole diameter of the spring hole 5 to the inner diameter of the main cavity 1 is in the range of 0.186 to 0.244. In the embodiment, the ratio of the hole diameter of the spring hole 5 to the inner diameter of the main cavity 1 is designed to be in the range of 0.186 to 0.244. If the hole diameter of the spring hole 5 is too large and exceeds the upper limit of the above range, while ensuring that the minimum distance between the spring hole 5 and the suction hole 2 meets the above requirements, the suction hole 2 will be farther away from the sliding vane groove 4, which will cause more refrigerant in the main cavity 1 to flow back to the suction pipe from the suction hole 2, resulting in a decrease in the suction amount and a decrease in the energy efficiency. If the hole diameter of the spring hole 5 is too small and below the lower limit of the above range, the spring matched therewith will be too thin, which not only requires a better fatigue life of the spring, but also the spring is prone to bending and deforming during installation, increasing the assembly difficulty. In the embodiment, by designing the ratio of the hole diameter of the spring hole 5 to the inner diameter of the main cavity 1 to be in the range of 0.186 to 0.244, the above two factors can be well balanced, and the compressor has a higher energy efficiency and a lower assembly difficulty.

[0034] In a specific embodiment, the hole diameter of the spring hole 5 is in the range of Φ8 mm to Φ9.5 mm, and the inner diameter of the main cavity 1 is in the range of Φ39 mm to Φ43 mm.

[0035] Preferably, the suction angle θ of the compressor cylinder is in the range of 21°≤θ≤25°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, and the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove 4 on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole 2.

[0036] In specific implementation, in order to improve the energy efficiency of the compressor to a greater extent, different suction angles θ can be preferred for spring holes 5 with different hole diameters, thereby improving the volumetric efficiency and the energy efficiency of the compressor. For example, the following embodiments have been confirmed by the applicant's targeted design and practice that the compressor cylinder designed with the following parameters can ensure a higher energy efficiency of the compressor and has a higher practical value.

[0037] For example, in an optional embodiment, the suction hole 2 has a hole diameter of 12 mm, the spring hole 5 has a hole diameter of 8 mm, and the suction angle θ of the compressor cylinder ranges from 21.5° to 23°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the slide groove 4 projected on the end surface of the compressor cylinder, and the second axis is the central axis of the suction hole 2.

[0038] In another optional embodiment, the suction hole 2 has a hole diameter of 12 mm, the spring hole 5 has a hole diameter of 8.5 mm, and the suction angle θ of the compressor cylinder ranges from 22° to 23.5°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the slide groove 4 projected on the end surface of the compressor cylinder, and the second axis is the central axis of the suction hole 2.

[0039] In another optional embodiment, the suction hole 2 has a hole diameter of 12 mm, the spring hole 5 has a hole diameter of 9 mm, and the suction angle θ of the compressor cylinder ranges from 22.5° to 24°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the slide groove 4 projected on the end surface of the compressor cylinder, and the second axis is the central axis of the suction hole 2.

[0040] In another optional embodiment, the suction hole 2 has a hole diameter of 12 mm, the spring hole 5 has a hole diameter of 9.5 mm, and the suction angle θ of the compressor cylinder ranges from 23° to 24.6°, wherein the suction angle θ of the compressor cylinder is the included angle between the first axis and the second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the slide groove 4 projected on the end surface of the compressor cylinder, and the second axis is the central axis of the suction hole 2.

[0041] In addition, the embodiment of the utility model provides a kind of rotor compressor, and rotor compressor includes above-mentioned compressor cylinder.Because rotor compressor has above-mentioned compressor cylinder, the minimum distance between spring hole 5 and suction hole 2 is optimized and designed by using the compressor cylinder with above-mentioned structure design, so that the minimum distance d between them satisfies 1.0 mm≤d≤1.7 mm.After using the size parameter design, it can avoid the case that the distance between spring hole 5 and suction hole 2 is too small to cause material deformation or rupture between them, and also can avoid the case that the distance between spring hole 5 and suction hole 2 is too large to cause suction hole 2 to be too far from slide groove 4, thereby causing performance reduction, can well balance the structural reliability and performance of compressor.

[0042] As Figure 3 Specifically, the compressor includes an upper bearing 60, a lower bearing 70 and a silencer 80, the compressor cylinder 10 is clamped and installed between the upper bearing 60 and the lower bearing 70, the silencer 80 is covered on the upper bearing 60, and the crankshaft 20 is arranged through the silencer 80, the upper bearing 60, the compressor cylinder 10 and the lower bearing 70.

[0043] Figure 5 When the embodiments of the compressor of the utility model adopt different wall thickness (the minimum distance d between the spring hole and the suction hole), the COP case schematic diagram is shown, wherein, COP (Coefficient of Performance) is the refrigeration cycle performance coefficient (also called refrigeration coefficient), which is used to evaluate the energy consumption index of the refrigeration cycle or the unit power refrigerating capacity of the compressor. It can be seen that the smaller the wall thickness (the minimum distance d between the spring hole and the suction hole) is, the greater the COP value is, the compressor cylinder of the embodiment of the utility model can ensure that the compressor has higher performance by designing the minimum distance d between the spring hole 5 and the suction hole 2 as 1.0mm≤d≤1.7mm, and the strength problem caused by too small wall thickness can be avoided, and the service life of the compressor can be ensured.

[0044] From the above description, it can be seen that the above-mentioned embodiments of the utility model realize the following technical effects:

[0045] The embodiment of the utility model discloses: main cavity 1 is set up on the compressor cylinder, and the main cavity 1 is along the axial penetration compressor cylinder and is arranged, suction hole 2 and exhaust hole 3, suction hole 2 and exhaust hole 3 all communicate with main cavity 1, and suction hole 2 and exhaust hole 3 are along the circumferential interval of compressor cylinder and are arranged, sliding vane groove 4 is along the circumferential of compressor cylinder, and sliding vane groove 4 is arranged between suction hole 2 and exhaust hole 3, spring hole 5, spring hole 5 is interval arranged with main cavity 1, and spring hole 5 communicates with sliding vane groove 4, and the minimum distance d between spring hole 5 and suction hole 2 satisfies: 1.0mm <= d <= 1.7mm. Because spring hole 5 communicates with sliding vane groove 4, and the aperture arm sliding vane groove 4 along the width of compressor cylinder is big, therefore spring hole 5 will cause the influence to the relative position arrangement between sliding vane groove 4 and suction hole 2, and the compressor cylinder in the related art only considers the distance between sliding vane groove 4 and suction hole 2, and does not consider the influence of spring hole 5 to the arrangement between the both, leading to the unreasonable parameter design, and the designed compressor is difficult to take into account the structural reliability and the requirement of high energy efficiency. The compressor cylinder with the above structure design carries out the optimal design to the minimum distance between spring hole 5 and suction hole 2, and makes the minimum distance d between the both satisfy 1.0mm <= d <= 1.7mm. After using this size parameter design, can avoid the condition that the distance between spring hole 5 and suction hole 2 is too small and leads to the material deformation or rupture between the both, also can avoid the condition that the distance between spring hole 5 and suction hole 2 is too big and leads to suction hole 2 to be too far from sliding vane groove 4, thereby leading to the performance reduction, can take into account the structural reliability and the performance of compressor well.

[0046] For ease of description, spatial relative terms, such as "above", "upper", "top", "up", and the like, can be used herein to describe the spatial relationship between one device or feature and another device or feature as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "on" other devices or structures will be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below" orientations. The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein are interpreted accordingly.

[0047] It is to be understood that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0048] It should be noted that the terms "first", "second", and the like, used in the specification and in the claims of the application, as well as above-described appended drawings, are used to distinguish similar objects and are not necessarily used to describe a specific sequence or chronology. It should be understood that the data used in this way can be interchanged as appropriate, so that the embodiments of the application described herein can be implemented, for example, in an order other than that illustrated or described herein. In addition, the terms "comprise" and "have" and any variations thereof, are intended to cover non-exclusive inclusion, for example, a process, method, system, product, or apparatus that includes a list of steps or units is not necessarily limited to those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to such processes, methods, products, or apparatuses.

[0049] The preferred embodiments of the application are described above, and are not intended to limit the application. The application can be modified and changed by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the application shall be included in the protection scope of the application.

Claims

1. A compressor cylinder characterized by, The compressor cylinder is provided with: a main cavity (1) arranged through the compressor cylinder along the axial direction of the compressor cylinder; an air inlet hole (2) and an air outlet hole (3) both communicating with the main cavity (1) and arranged at intervals along the circumferential direction of the compressor cylinder; a sliding vane groove (4) arranged between the air inlet hole (2) and the air outlet hole (3) along the circumferential direction of the compressor cylinder; a spring hole (5) arranged at intervals with the main cavity (1) and communicating with the sliding vane groove (4); the minimum distance d between the spring hole (5) and the air inlet hole (2) satisfies 1.0mm≤d≤1.7mm.

2. The compressor cylinder of claim 1, wherein, The compressor cylinder is formed by a powder metallurgy process, and the width of the sliding vane groove (4) along the circumferential direction of the compressor cylinder is 2.8mm.

3. The compressor cylinder of claim 1, wherein, The ratio of the aperture of the spring hole (5) to the inner diameter of the main cavity (1) ranges from 0.186 to 0.

244.

4. The compressor cylinder of claim 3, wherein, The aperture of the spring hole (5) ranges from Φ8mm to Φ9.5mm, and the inner diameter of the main cavity (1) ranges from Φ39mm to Φ43mm.

5. The compressor cylinder of any one of claims 1 to 4, wherein, The air intake angle θ of the compressor cylinder ranges from 21° to 25°, wherein the air intake angle θ of the compressor cylinder is the included angle between a first axis and a second axis, both of which are arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove (4) on the end face of the compressor cylinder, and the second axis is the central axis of the air inlet hole (2).

6. The compressor cylinder of any one of claims 1 to 4, wherein, The aperture of the air inlet hole (2) is 12mm, the aperture of the spring hole (5) is 8mm, and the air intake angle θ of the compressor cylinder ranges from 21.5° to 23°, wherein the air intake angle θ of the compressor cylinder is the included angle between a first axis and a second axis, both of which are arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove (4) on the end face of the compressor cylinder, and the second axis is the central axis of the air inlet hole (2).

7. The compressor cylinder of any one of claims 1 to 4, wherein, The aperture of the air inlet hole (2) is 12mm, the aperture of the spring hole (5) is 8.5mm, and the air intake angle θ of the compressor cylinder ranges from 22° to 23.5°, wherein the air intake angle θ of the compressor cylinder is the included angle between a first axis and a second axis, both of which are arranged along the radial direction of the compressor cylinder, the first axis is the symmetry axis of the projection of the sliding vane groove (4) on the end face of the compressor cylinder, and the second axis is the central axis of the air inlet hole (2).

8. The compressor cylinder of any one of claims 1 to 4, wherein, The suction hole (2) has a hole diameter of 12 mm, the spring hole (5) has a hole diameter of 9 mm, and the suction angle θ of the compressor cylinder ranges from 22.5° to 24°, wherein the suction angle θ of the compressor cylinder is the included angle between a first axis and a second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the axis of symmetry of the projection of the sliding vane groove (4) on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole (2).

9. The compressor cylinder of any one of claims 1 to 4, wherein, The suction hole (2) has a hole diameter of 12 mm, the spring hole (5) has a hole diameter of 9.5 mm, and the suction angle θ of the compressor cylinder ranges from 23° to 24.6°, wherein the suction angle θ of the compressor cylinder is the included angle between a first axis and a second axis, the first axis and the second axis are both arranged along the radial direction of the compressor cylinder, the first axis is the axis of symmetry of the projection of the sliding vane groove (4) on the end face of the compressor cylinder, and the second axis is the central axis of the suction hole (2).

10. A rotary compressor characterized by The rotor compressor comprises the compressor cylinder according to any one of claims 1 to 9.

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