Cylinder, pump body assembly and rotary compressor

Abstract

The application provides a cylinder, a pump body assembly and a rotary compressor. The cylinder comprises a cylinder body (1), a pressure relief groove (2) and a sliding vane groove (3) are arranged on the cylinder body (1), the sliding vane groove (3) extends along the radial direction of the cylinder body (1), and the pressure relief groove (2) is arranged on the inner wall surface of the cylinder body (1). In a cross section perpendicular to the central axis of the cylinder body (1), a line between the end point of the starting end of the pressure relief groove (2) away from the sliding vane groove (3) and the central axis of the cylinder body (1) is a first line, an included angle θ is formed between the first line and the center line of the sliding vane groove (3), and 21°≤θ≤90°. The cylinder provided by the technical scheme of the application can solve the problem that the oil compression of the compressor pump body is excessive during a vacuum limit reliability test, and the reliability test requirements cannot be met.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air compression equipment, in particular to a cylinder, a pump body assembly and a rotary compressor. BACKGROUND

[0002] With the development of rotary compressor technology, the displacement of rotary compressors has been expanded to more than 100cc, which can meet the cooling capacity demand of more than 20hp of air conditioning systems, and the development demand of large-displacement rotary compressors is strong. In the design of extreme displacement compressors, it is found that the conventional double-rotor compressor structure cannot meet the design requirements of large-displacement compressors. The single cylinder displacement of the compressor pump body is large, and the cylinder height is high. It is found in the product development process that the anti-hydraulic pressure capacity is far inferior to that of conventional rotary compressors under the conditions of vacuum limit and serious liquid carrying, and the compressor has serious reliability problems.

[0003] At present, the mass production of compressor products must meet the requirements of vacuum limit experiments. The vacuum limit experiment mainly simulates the reliability problems of the compressor when the capillary tube of the air conditioning system is frozen or the small valve is forgotten to open when the compressor rapidly increases the frequency. For small-displacement compressors, due to the small displacement, the vacuum pumping capacity is limited, and under the same leakage gap, the compressor pump body pumping and leakage through the gap between the roller and the end face of the cylinder, the slide groove and the radial gap between the roller and the cylinder reach a balanced state. The compressor completes multiple vacuum state operations under the required working conditions. After dissection, the compressor has no wear and passes the reliability experiment. The pumping capacity of small-displacement compressors is limited, and they can generally meet the requirements of the reliability experiment.

[0004] However, for large-displacement compressors, the displacement is large, the cylinder height is high, and the compressor pumping capacity is strong. During the vacuum limit experiment, the pump body suction chamber is close to 0Pa pressure, and the exhaust chamber and back pressure chamber are above 2.5Mpa high pressure. Under such a large pressure difference, the lubricating oil in the compressor shell enters the suction chamber through the leakage gap of the pump body. During the compression process, the lubricating oil is a liquid incompressible medium, and too much lubricating oil in the suction chamber and compression chamber will cause serious liquid compression. The volume of the compression chamber at the exhaust tail is very small, and the lubricating oil is incompressible, which will make the pressure in the chamber very high. The instantaneous increase of the load of the compressor will cause bearing wear and large current protection shutdown. After multiple test cycles, the disassembled compressor will have abnormal wear of the roller end face and the partition plate, the test will be unqualified, and the compressor cannot be mass produced. This problem is a common difficult problem in the development of large-displacement compressor products in the industry. SUMMARY

[0005] The main purpose of the present application is to provide a cylinder, a pump body assembly and a rotary compressor, which can solve the problem of over-compression of the compressor pump body oil during the vacuum limit reliability test, and cannot meet the requirements of the reliability test.

[0006] In order to achieve the above object, according to one aspect of the present application, there is provided a cylinder comprising a cylinder body, wherein a pressure relief groove and a sliding vane groove are arranged on the cylinder body, the sliding vane groove extends along a radial direction of the cylinder body, and the pressure relief groove is arranged on an inner wall surface of the cylinder body; in a cross section perpendicular to a central axis of the cylinder body, a first line is defined between an end point of a starting end of the sliding vane groove and the central axis of the cylinder body, a second line is defined between an end point of the pressure relief groove and the central axis of the cylinder body, and an included angle θ is formed between the first line and a center line of the sliding vane groove, wherein 21°≤θ≤90°.

[0007] Further, 25°≤θ≤60°.

[0008] Further, 30°≤θ≤50°.

[0009] Further, a chamfer groove is arranged on the cylinder body, in the cross section perpendicular to the central axis of the cylinder body, a third line is defined between the end point of the starting end of the sliding vane groove and the central axis of the cylinder body, a fourth line is defined between an end point of the pressure relief groove and the central axis of the cylinder body, and an included angle θ1 is formed between the second line and the center line of the sliding vane groove, wherein θ1≤θ2.

[0010] Further, the end point of the pressure relief groove is in communication with the sliding vane groove.

[0011] Further, the pressure relief groove extends along the inner wall surface of the cylinder body towards the sliding vane groove.

[0012] Further, along an extension direction close to the sliding vane groove, a radial depth of the pressure relief groove is constant, or, along the extension direction close to the sliding vane groove, the radial depth of the pressure relief groove increases, or, along the extension direction close to the sliding vane groove, the radial depth of the pressure relief groove decreases.

[0013] Further, along an axial direction of the cylinder body, the pressure relief groove is arranged at a middle position of the inner wall surface of the cylinder body.

[0014] Further, a chamfer groove is arranged on the cylinder body, the pressure relief groove extends to the chamfer groove and is in communication with the chamfer groove.

[0015] Further, a volume of the pressure relief groove at the middle position of the inner wall surface of the cylinder body is V1, and a displacement of the cylinder is V, wherein V1 / V≤2%.

[0016] Further, a chamfer groove and a resonance cavity are arranged on the cylinder body, the resonance cavity is arranged on a side of the chamfer groove away from the inner wall of the cylinder body and is in communication with the chamfer groove, and one end of the pressure relief groove is located on the inner wall of the cylinder body and extends obliquely along an end surface of the cylinder body on which the chamfer groove is located to the resonance cavity.

[0017] According to another aspect of the present application, there is provided a pump body assembly comprising a cylinder, wherein the cylinder is the cylinder as described above.

[0018] Further, the pump body assembly further comprises a crankshaft, a roller, a sliding vane, an upper flange and a lower flange, the upper flange, the roller and the lower flange are sleeved on the crankshaft, the roller is arranged in the inner cavity of the cylinder body, and the sliding vane is slidingly arranged in the sliding vane groove.

[0019] According to another aspect of the present application, a rotary compressor is provided, comprising the cylinder or the pump body assembly.

[0020] According to the technical scheme of the present application, the cylinder comprises a cylinder body, the cylinder body is provided with a pressure relief groove and a sliding vane groove, the sliding vane groove extends along the radial direction of the cylinder body, the pressure relief groove is arranged on the inner wall surface of the cylinder body, in a cross section perpendicular to the central axis of the cylinder body, a line between the end point of the starting end of the pressure relief groove away from the sliding vane groove and the central axis of the cylinder body is a first line, an included angle θ between the first line and the center line of the sliding vane groove is formed, and 21°≤θ≤90°. The cylinder can connect the high pressure in the compression chamber and the low pressure in the suction chamber through the pressure relief groove arranged on the inner wall surface of the cylinder body and the starting point position of the pressure relief groove, and the high pressure oil pressure in the compression chamber is discharged to the suction chamber in advance under the premise of avoiding excessive influence on the performance of the compressor, so as to realize the advance of the tail relief angle, so that the compression oil phenomenon does not occur in the operation process of the compressor, thereby effectively solving the problem of over-compression of the compressor pump body during the vacuum limit reliability test, and ensuring the reliability of the compressor. BRIEF DESCRIPTION OF DRAWINGS

[0021] The drawings accompanying the specification of this application form a part thereof, serve to provide further understanding of the present application, and together with the description of the exemplary embodiments of the present application, serve to explain the present application, and do not constitute improper limitations on the present application. In the drawings:

[0022] Figure 1 A perspective structural schematic view of a cylinder of an embodiment of the present application is shown;

[0023] Figure 2 An enlarged structural schematic view of A of Figure 1 is shown;

[0024] Figure 3 A structural view of a pump body assembly of an embodiment of the present application is shown;

[0025] Figure 4 A sectional structural schematic view of A-A of Figure 3 is shown;

[0026] Figure 5 An enlarged structural schematic view of B of Figure 4 is shown;

[0027] Figure 6 A size structural view of a pressure relief groove of a cylinder of an embodiment of the present application is shown;

[0028] Figure 7An enlarged structural schematic view at C of Figure 6 ;

[0029] Figure 8 A compressor pump body compression chamber volume curve changing with crank angle of an embodiment of the application is shown; and

[0030] Figure 9 A Pθ curve comparison diagram of suction chamber and compression chamber pressure changing with angle of a compressor pump body with and without pressure relief groove is shown.

[0031] Wherein, the above drawings include the following reference signs:

[0032] 1, cylinder; 2, pressure relief groove; 3, sliding vane groove; 4, bevel groove; 5, resonance cavity; 6, crankshaft; 7, roller; 8, sliding vane; 9, upper flange; 10, lower flange. DETAILED DESCRIPTION

[0033] 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.

[0034] In the development process of large displacement double-rotor compressor products, it is found that large displacement compressors are difficult to pass the vacuum limit experiment requirement, and the reliability cannot meet the product test requirement. According to the existing conventional design scheme, when the vacuum limit test is performed, large current protection shutdown basically occurs, and after dissection, the compressor appears wear between the roller end face and the end face of the partition plate and the bearing. The analysis shows that the main reason is that, at the vacuum limit, the suction chamber pressure is close to vacuum 0 Pa, and the shell back pressure chamber pressure is 2.5 MPa or above. Under such a large pressure difference, the lubricating oil is sucked into the pump body suction chamber and compression chamber. Since the pump body suction chamber and compression chamber have small volume, after a certain period of operation in the vacuum limit experiment, the suction chamber and compression chamber are filled with lubricating oil. At this time, the hydraulic compression of the compressor is very serious, especially when the radial gap between the outer diameter of the roller and the inner diameter of the cylinder and the exhaust tail volume are very small. The high pressure oil generates high pressure and then generates instantaneous large load, which causes the load of the compressor to suddenly increase, and the pump body appears abnormal wear. During the vacuum limit experiment, it is found that there is non-periodic instantaneous high pressure in the exhaust tail through monitoring the compression chamber pressure. Due to the limited sensor collection position, there may be higher pressure oil pressure at the radial gap between the roller and the cylinder.

[0035] In order to solve this problem, the inventors have carried out experimental research on various schemes for this problem, and found that when the vacuum degree in the suction chamber is too high after the suction valve is closed, the compressor is prone to abnormal wear. However, if there is a certain suction pressure in the suction chamber, the compressor can normally complete the vacuum limit experiment and there is no wear after dissection. Based on this feature, the present application proposes a new cylinder.

[0036] For referenceFigures 1 to 9 As shown, according to the embodiment of the present application, the cylinder comprises a cylinder body 1, the cylinder body 1 is provided with a pressure relief groove 2 and a sliding vane groove 3, the sliding vane groove 3 extends along the radial direction of the cylinder body 1, the pressure relief groove 2 is arranged on the inner wall surface of the cylinder body 1, in the cross section perpendicular to the central axis of the cylinder body 1, the line between the end point of the starting point of the pressure relief groove 2 and the central axis of the cylinder body 1 is a first line, an included angle θ is formed between the first line and the center line of the sliding vane groove 3, 21°≤θ≤90°.

[0037] The cylinder can make the pressure relief groove 2 connect the high pressure in the compression chamber with the low pressure in the suction chamber, and the high pressure oil pressure in the compression chamber is discharged to the suction chamber in advance, the tail pressure relief angle is advanced, the compression chamber is not in the state of oil compression during the operation of the compressor, the problem of oil compression in the tail of the exhaust gas is solved by discharging in advance, the problem of over-compression of the compressor pump body during the vacuum limit reliability test is effectively solved, and the wear problem caused by over-compression of the vacuum limit is solved, thereby ensuring the reliability of the compressor.

[0038] In one embodiment, 25°≤θ≤60°, the starting point position of the pressure relief groove 2 can be advanced to 335°, so that the minimum design of the pressure relief angle is 300°, and the maximum design is 335°, and the pressure relief angle of the conventional design without pressure relief groove is 340°, therefore, the pressure relief groove 2 formed by the above design makes the tail pressure relief angle of the compressor take a value between 300° and 335°, and the pressure relief angle is at least 5° earlier than the conventional scheme by using the pressure relief groove 2, so that the compression chamber and the suction chamber are timely connected, the high pressure oil pressure in the compression chamber is discharged to the suction chamber in advance, the oil compression phenomenon is avoided, and the wear problem caused by over-compression of the vacuum limit is effectively avoided.

[0039] In one embodiment, 30°≤θ≤50°, when the starting point of the pressure relief groove 2 is designed according to the angle, the formed pressure relief angle takes a value between 310° and 330°, and is preferably 320°, in this angle range, the performance of the compressor is reduced to the minimum, the occurrence of the oil compression problem is avoided to the maximum, and the comprehensive performance of the working performance and the reliability of the compressor is best.

[0040] For reference Figure 8As shown in the figure, the rotor compressor pump body compression chamber volume changes with the rotor angle curve, the compression chamber volume is very small after the crankshaft angle turns through 320°, and the change of the compression chamber volume after the angle is also very small, so the part of the volume is not much affected by the compressor performance when the pressure is released in advance, and the compression chamber can be connected with the suction chamber and the pressure chamber in time before the oil pressure phenomenon occurs. When the crankshaft angle reaches 330°, the compression chamber volume accounts for only 1.8% of the total volume of the cylinder, and the part of the volume is at the end of the exhaust time, and the exhaust volume is very small. At this position, the pressure is released, which basically does not affect the performance of the compressor.

[0041] For reference Figure 9 As shown in the figure, the rotor compressor pump body compression chamber volume changes with the rotor angle curve, the compression chamber volume is very small after the crankshaft angle turns through 320°, and the change of the compression chamber volume after the angle is also very small, so the part of the volume is not much affected by the compressor performance when the pressure is released in advance, and the compression chamber can be connected with the suction chamber and the pressure chamber in time before the oil pressure phenomenon occurs. When the crankshaft angle reaches 330°, the compression chamber volume accounts for only 1.8% of the total volume of the cylinder, and the part of the volume is at the end of the exhaust time, and the exhaust volume is very small. At this position, the pressure is released, which basically does not affect the performance of the compressor.

[0042] For reference Figure 9 It can be seen that when the pressure relief angle is advanced to about 320°, whether from the retention of the compressor performance or from the avoidance of the oil pressure phenomenon of the compressor, good results can be obtained, so the effect of the pressure relief angle at 320° is best in comprehensive consideration.

[0043] In one embodiment, the cylinder body 1 is also provided with a chamfered groove 4, the line between the end point of the pressure relief groove 2 and the center axis of the cylinder body 1 is a second line, the second line and the center line of the sliding vane groove 3 form an included angle θ1, the line between the starting end point of the chamfered groove 4 away from the sliding vane groove 3 and the center axis of the cylinder body 1 is a third line, the third line and the center line of the sliding vane groove 3 form an included angle θ2, θ1≤θ2. The chamfered groove 4 can form a crescent cavity on the cylinder body 1 to facilitate the exhaust of the compressor.

[0044] In this embodiment, since θ1≤θ2, the end of the pressure relief groove 2 can be located on the side of the chamfered groove 4 close to the sliding vane groove 3, or the starting end of the chamfered groove 4 coincides with the position in the circumferential direction, so that the pressure relief process of the pressure relief groove 2 can be connected with the pressure relief process of the chamfered groove 4 in the circumferential direction of the cylinder body 1, forming a continuous pressure relief effect, the pressure relief effect has good continuity, which can more effectively avoid the oil pressure problem during the operation of the compressor, and ensure the operation reliability of the compressor.

[0045] In one embodiment, the end of the pressure relief groove 2 communicates with the sliding vane groove 3, so that the pressure relief groove 2 partially overlaps with the pressure relief path formed by the pressure relief groove 2 and the bevel groove 4, which can ensure the continuity of the pressure relief process and improve the pressure relief capacity by double or multiple pressure relief.

[0046] In one embodiment, the pressure relief groove 2 extends along the inner wall surface of the cylinder body 1 towards the sliding vane groove 3. In this embodiment, the pressure relief groove 2 forms a continuous extension along the inner wall surface of the cylinder body 1, so that the compression chamber can always communicate with the suction chamber through the sliding vane groove 3 after the roller 7 reaches the pressure relief groove 2 during the sliding process of the roller 7 along the inner wall surface of the cylinder body 1, thereby avoiding the problem of oil compression during the operation of the compressor.

[0047] In one embodiment, the radial depth of the pressure relief groove 2 is constant along the extension direction close to the sliding vane groove 3.

[0048] In one embodiment, the radial depth of the pressure relief groove 2 increases along the extension direction close to the sliding vane groove 3.

[0049] In one embodiment, the radial depth of the pressure relief groove 2 decreases along the extension direction close to the sliding vane groove 3.

[0050] In one embodiment, the pressure relief groove 2 is arranged at the middle position of the inner wall surface of the cylinder body 1 along the axial direction of the cylinder body 1. In this embodiment, the pressure relief groove 2 is arranged at the middle position of the inner wall surface of the cylinder body 1 along the axial direction, so that the compression chambers at both ends of the cylinder body 1 can communicate with the suction chamber through the pressure relief groove 2, and the spaces of the compression chambers at both ends of the pressure relief groove 2 can be equally divided, thereby enabling the high-pressure oil in the compression chambers at both ends of the pressure relief groove 2 to be evenly relieved through the pressure relief groove 2, ensuring stable pressure changes at both ends of the pressure relief groove 2 during the pressure relief process, good pressure relief performance, and effectively reducing the impact of the arrangement of the pressure relief groove 2 on the performance of the compressor.

[0051] In one embodiment, the cylinder body 1 is further provided with a bevel groove 4, and the pressure relief groove 2 extends to the bevel groove 4 and communicates with the bevel groove 4. In this embodiment, the pressure relief groove 2 is arranged on the inner wall surface of the cylinder body 1 and located at one end of the cylinder body 1 where the bevel groove 4 is arranged, i.e., the pressure relief groove 2 is arranged at one end of the inner wall surface of the cylinder body 1 close to the bevel groove 4, thereby facilitating the communication between the pressure relief groove 2 and the bevel groove 4. Since the pressure relief groove 2 communicates with the bevel groove 4, continuous pressure relief from the pressure relief groove 2 to the bevel groove 4 can be achieved after the compressor forms pressure relief by the pressure relief groove 2, the pressure relief process is more stable and continuous, and the pressure relief effect is better.

[0052] In one embodiment, the volume of the pressure relief groove 2 located at the middle position of the inner wall surface of the cylinder body 1 is V1, the displacement of the cylinder is V, and V1 / V≤2%, which can effectively reduce the residual volume generated by the pressure relief groove 2 and ensure the compression performance of the compressor while ensuring the pressure relief function of the pressure relief groove 2.

[0053] In one embodiment, the cylinder body 1 is further provided with a chamfered groove 4 and a resonance cavity 5, the resonance cavity 5 is located at the side of the chamfered groove 4 away from the inner wall of the cylinder body 1 and communicates with the chamfered groove 4, and the pressure relief groove 2 is located on the end surface of the cylinder body 1 where the chamfered groove 4 is located and extends obliquely along the end surface of the cylinder body 1 to the resonance cavity 5.

[0054] In this embodiment, the pressure relief groove 2 is located on the end surface of the cylinder body 1 and communicates with the chamfered groove 4 through the resonance cavity 5, which can realize continuous pressure relief function and effectively avoid the phenomenon of oil compression.

[0055] According to the embodiment of the present application, the pump body assembly comprises a cylinder, which is the above-mentioned cylinder.

[0056] In one embodiment, the pump body assembly further comprises a crankshaft 6, a roller 7, a sliding vane 8, an upper flange 9 and a lower flange 10, the upper flange 9, the roller 7 and the lower flange 10 are all sleeved on the crankshaft 6, the roller 7 is arranged in the inner cavity of the cylinder body 1, and the sliding vane 8 is slidingly arranged in the sliding vane groove 3.

[0057] In this embodiment, the roller 7 is installed on the eccentric circle of the crankshaft 6, the sliding vane 8 is installed in the sliding vane groove 3 of the cylinder body 1, and the roller 7, the sliding vane 8 and the minimum radial gap between the roller 7 and the cylinder body 1 divide the working cavity of the cylinder body 1 into a compression cavity and a suction cavity, and the volumes of the compression cavity and the suction cavity change periodically with the rotation of the crankshaft 6. Figure 7 As shown in the structure of the cylinder end surface pressure relief, when the minimum radial gap between the roller 7 and the cylinder body 1 passes through the pressure relief groove 2 of the cylinder end surface, the pressure relief starts, at this time, the suction cavity is low pressure and the compression cavity is high pressure, the chamfered groove 4 and the resonance cavity 5 communicate with the compression cavity, and under the action of the pressure difference, the high-pressure refrigerant and the lubricating oil mixture enter the suction cavity of the compressor pump body through the resonance cavity 5 and the pressure relief groove 2 of the cylinder end surface, and the tail over-compression pressure relief is completed.

[0058] In the vacuum limit experiment, the suction port of the compressor is closed, the suction cavity is always in a low pressure state close to vacuum, the compression cavity and the shell back pressure are in the exhaust pressure state, and the pressure difference can reach more than 2 MPa. Under this pressure difference, the lubricating oil in the lubricating oil circuit flows into the suction cavity and the compression cavity through the gap between the roller 7 and the end surface of the cylinder body and the gap between the sliding vane 8 and the sliding vane groove 3, and the compression cavity is filled with lubricating oil. Since the lubricating oil is a liquid and cannot be compressed, at this time, the compression cavity generates a transient high pressure, and then the pump body generates a transient large load, which causes the compressor to have a large current and is difficult to work normally. The high pressure oil in the compression cavity can be introduced into the low pressure suction cavity through the pressure relief groove 2 to meet the requirements of the vacuum limit reliability experiment.

[0059] The pressure relief mode of the pressure relief groove 2 in the middle of the cylinder body 1 is basically the same as that of the pressure relief groove 2 at the end surface of the cylinder body. When the minimum radial gap between the cylinder body 1 and the roller 7 rotates to the starting point of the pressure relief groove 2 in the middle of the cylinder body 1, since the large displacement compressor cylinder body 1 is high, during the vacuum limit experiment, as the compression cavity volume decreases, most of the lubricating oil is accumulated in the middle of the cylinder body 1 and is discharged through the minimum radial gap between the roller 7 and the cylinder body 1. In order to ensure the performance of the compressor, the radial gap is generally designed to be small. During the vacuum limit experiment, a large amount of lubricating oil is difficult to discharge through the minimum radial gap between the roller and the cylinder body 1, which causes the lubricating oil pressure at this position to rise sharply and generates a transient large load. Through the pressure relief groove 2 in the middle of the cylinder body 1, when the minimum radial gap between the roller 7 and the cylinder body 1 rotates through the starting point of the pressure relief groove 2 in the middle of the cylinder body 1, the high pressure in the compression cavity and the low pressure in the suction cavity begin to communicate through the pressure relief groove 2 in the middle of the cylinder body 1, and the high pressure oil gas mixture is discharged to the suction cavity through the pressure relief groove 2 in the middle of the cylinder body 1. Since the suction cavity is connected with the distributor, the lubricating oil leaked into the suction cavity can enter the internal storage of the distributor, thereby solving the problem of over-compression of the oil in the pump body during the vacuum limit reliability experiment.

[0060] According to the embodiment of the application, the rotary compressor comprises the cylinder or the pump body assembly as described above.

[0061] It is to be noted that the terms used herein are only for the purpose of describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that, when the terms "comprise" and / or "include" are used in the specification, there is a presence of the features, steps, operations, devices, components and / or combinations thereof.

[0062] It should be noted that the terms "first", "second", and the like, used in the description and in the claims of the present application as well as above-mentioned figures are used to distinguish between similar objects and not necessarily for describing a specific sequential or chronological order. It is to be understood that the use of data so designated is not meant to limit a given item described by such data to the same category as other data designated by the same designations, but instead is so designated only for convenience as a means of discriminating between the two series of items that refer to a same data.

[0063] The preferred embodiments of the application described herein are examples of the present application and are not intended to limit the scope of the application. Various modifications and changes can be made thereto by those skilled in the art which freely adapt to the idea and principles of the application, without departing from the spirit and scope thereof, and it is to be understood that such modifications and changes are to be included within the scope of the application as defined by the appended claims.

Claims

1. A cylinder, characterized in that, Includes a cylinder body (1), on which a pressure relief groove (2) and a sliding vane groove (3) are provided. The sliding vane groove (3) extends radially along the cylinder body (1). The pressure relief groove (2) is disposed on the inner wall surface of the cylinder body (1). On a cross-section perpendicular to the central axis of the cylinder body (1), the line connecting the starting end of the pressure relief groove (2) away from the sliding vane groove (3) and the central axis of the cylinder body (1) is a first line. The first line forms an angle θ with the center line of the sliding vane groove (3), where 21°≤θ≤90°. The pressure relief groove (2) can connect the cylinder body (1). 1) The compression chamber is high pressure and the intake chamber is low pressure; the cylinder body (1) is also provided with a chamfered groove (4). On the cross section perpendicular to the central axis of the cylinder body (1), the line connecting the end point of the pressure relief groove (2) and the central axis of the cylinder body (1) is the second line. The second line forms an angle θ1 with the center line of the sliding vane groove (3). The line connecting the beginning end point of the chamfered groove (4) away from the sliding vane groove (3) and the central axis of the cylinder body (1) is the third line. The third line forms an angle θ2 with the center line of the sliding vane groove (3). θ1≤θ2.

2. The cylinder according to claim 1, characterized in that, 25°≤θ≤60°.

3. The cylinder according to claim 2, characterized in that, 30°≤θ≤50°.

4. The cylinder according to claim 1, characterized in that, The end of the pressure relief groove (2) is connected to the sliding plate groove (3).

5. The cylinder according to any one of claims 1 to 3, characterized in that, The pressure relief groove (2) extends along the inner wall of the cylinder (1) toward the sliding vane groove (3).

6. The cylinder according to claim 5, characterized in that, The radial depth of the pressure relief groove (2) is constant along the extension direction close to the slide groove (3); or the radial depth of the pressure relief groove (2) increases along the extension direction close to the slide groove (3); or the radial depth of the pressure relief groove (2) decreases along the extension direction close to the slide groove (3).

7. The cylinder according to claim 6, characterized in that, Along the axial direction of the cylinder (1), the pressure relief groove (2) is located at the middle position of the inner wall surface of the cylinder (1).

8. The cylinder according to claim 5, characterized in that, The cylinder body (1) is also provided with a beveled groove (4), and the pressure relief groove (2) extends to the beveled groove (4) and communicates with the beveled groove (4).

9. The cylinder according to claim 7, characterized in that, The volume of the pressure relief groove (2) is V1, the displacement of the cylinder is V, and V1 / V≤2%.

10. The cylinder according to any one of claims 1 to 3, characterized in that, The cylinder (1) is also provided with a chamfered groove (4) and a resonant cavity (5). The resonant cavity (5) is located on the side of the chamfered groove (4) away from the inner wall of the cylinder (1) and is connected to the chamfered groove (4). One end of the pressure relief groove (2) is located on the inner wall of the cylinder (1) and extends obliquely from the inner wall of the cylinder (1) along the end face where the chamfered groove of the cylinder (1) is located to the resonant cavity (5).

11. A pump body assembly, comprising a cylinder, characterized in that, The cylinder is the cylinder according to any one of claims 1 to 10.

12. The pump body assembly according to claim 11, characterized in that, The pump body assembly also includes a crankshaft (6), rollers (7), vanes (8), an upper flange (9) and a lower flange (10). The upper flange (9), the rollers (7) and the lower flange (10) are all fitted on the crankshaft (6). The rollers (7) are disposed in the inner cavity of the cylinder (1). The vanes (8) are slidably disposed in the vane groove (3).

13. A rotary compressor, characterized in that, Includes the cylinder according to any one of claims 1 to 10 or the pump assembly according to claim 11 or 12.

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