Compressor slip sheet and rolling rotor compressor with same

Abstract

The utility model provides a compressor slip sheet and a rolling rotor type compressor with the same. The compressor slip sheet is provided with a first side face, a second side face opposite to the first side face, a head and a tail, the first side face and the second side face are used for being matched with a slip sheet groove of a compressor air cylinder, the first side face is arranged close to an air inlet of the compressor air cylinder, and the second side face is arranged close to an exhaust port of the compressor air cylinder. The first side face is provided with a first lubricating area close to the head, and the first lubricating area is provided with a first concave part used for containing a lubricating medium. And / or the second side face is provided with a second lubricating area close to the tail portion, and the second lubricating area is provided with a second concave portion used for containing the lubricating medium. The rotor type compressor effectively solves the problem that the energy efficiency of the compressor is affected due to the fact that the slip sheet of the rotor type compressor in the prior art is easy to abrade.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to a compressor vane and a rolling rotor compressor having therein. Background Technology

[0002] Currently, in traditional rotary compressors, the vane is a key moving component, and its design and material selection directly affect the compressor's performance and reliability. In existing technology, when the vane reciprocates radially within the cylinder vane slot, its head is in close contact with the outer cylindrical surface of the roller, dividing the cylinder's working area into the intake side and the compression side.

[0003] However, as the vane extends into the cylinder, it is subjected to unbalanced gas forces from both sides, causing the vane to become non-parallel to the vane slot, i.e., the vane is tilted. In this tilted state, the two sides of the vane form a wedge-shaped contact with the corresponding cylinder vane slot wall, generating a solid contact force. This solid contact force leads to greater wear on the vane, affecting not only its service life but also the compressor's energy efficiency and reliability. Utility Model Content

[0004] The main objective of this invention is to provide a compressor vane and a rolling rotor compressor having the same, so as to solve the problem that the vanes of the existing rotor compressor are prone to wear, which affects the energy efficiency of the compressor.

[0005] To achieve the above objectives, according to one aspect of the present invention, a compressor vane is provided. The compressor vane has a first side, a second side disposed opposite to the first side, a head, and a tail. Both the first and second sides are used to cooperate with a vane groove of a compressor cylinder. The first side is disposed near the air inlet of the compressor cylinder, and the second side is disposed near the exhaust port of the compressor cylinder. The first side has a first lubrication area disposed near the head, and the first lubrication area has a first recess for receiving a lubricating medium. And / or, the second side has a second lubrication area disposed near the tail, and the second lubrication area has a second recess for receiving a lubricating medium.

[0006] Furthermore, the first recess includes a plurality of first sub-recesses, which are spaced apart along the length and / or height direction of the compressor vane; and / or, the second recess includes a plurality of second sub-recesses, which are spaced apart along the length and / or height direction of the compressor vane.

[0007] Furthermore, the first sub-recess is at least one of a groove, a blind hole, and a through hole; and / or, the second sub-recess is at least one of a groove, a blind hole, and a through hole.

[0008] Furthermore, the total area s1 of the first recess and the total area S1 of the first lubrication zone satisfy the following condition: 0.05S1≤s1≤0.3S1; and / or, the total area s2 of the second recess and the total area S2 of the second lubrication zone satisfy the following condition: 0.05S2≤s2≤0.3S2.

[0009] Furthermore, the depth d1 of the first recess is greater than or equal to 5 μm and less than or equal to 100 μm; and / or, the depth d1 of the second recess is greater than or equal to 5 μm and less than or equal to 100 μm.

[0010] Furthermore, the first boundary of the first lubrication zone has a first distance y1 between it and the head, and the second boundary of the first lubrication zone has a second distance y2 between it and the head. The first distance y1 and the second distance y2 satisfy the following: 2e≤y2≤L2; where R is the inner diameter of the compressor cylinder, r is the outer diameter of the roller, and e is the eccentricity of the compressor. If the support reaction force at the first side is less than the support reaction force at the second side, the range of the compressor crankshaft angle is α1≤θ≤α2. When the support reaction force at the first side is greater than the support reaction force at the second side, the range of the compressor crankshaft angle is α2<θ≤α3; R h L1 is the radius of the arc of the head, and L2 is the length of the slider groove.

[0011] Furthermore, there is a third distance y3 between the first boundary of the second lubrication zone and the tail, and a fourth distance y4 between the second boundary of the second lubrication zone and the tail. The third distance y3 and the fourth distance y4 satisfy the following: ;

[0012] ;like Then y3≥0 is satisfied; L1 is the length of the compressor vane.

[0013] Further, each first sub-recess is a circular hole; or, the plurality of first sub-recesses include groups of first sub-recesses spaced apart along the length direction of the compressor vane, each group of first sub-recesses including a plurality of first extending recesses and a plurality of second extending recesses spaced apart or connected sequentially along the height direction of the compressor vane, a second extending recess is provided between each pair of adjacent first extending recesses, and a first extending recess is provided between each pair of adjacent second extending recesses; the sliding direction of the compressor vane is set at a first angle with the extending direction of each first extending recess and the extending direction of each second extending recess, and the extending direction of the first extending recess is set at a second angle with the extending direction of the second extending recess.

[0014] Further, each second sub-recess is a circular hole; or, the plurality of second sub-recesses include groups of second sub-recesses spaced apart along the length direction of the compressor vane, each group of second sub-recesses including a plurality of third extending recesses and a plurality of fourth extending recesses spaced apart or connected sequentially along the height direction of the compressor vane, a fourth extending recess is provided between each pair of adjacent third extending recesses, and a third extending recess is provided between each pair of adjacent fourth extending recesses; the sliding direction of the compressor vane is set at a third angle with the extending direction of each third extending recess and the extending direction of each fourth extending recess, and the extending direction of the third extending recess is set at a fourth angle with the extending direction of the fourth extending recess.

[0015] Furthermore, the compressor vanes are made of insulating material.

[0016] According to another aspect of the present invention, a rolling rotor compressor is provided, comprising: a pump body assembly including a compressor cylinder, rollers, and compressor vanes, wherein the rollers are rotatably disposed within the compressor cylinder, the compressor cylinder having vane grooves, and the compressor vanes being slidably disposed within the vane grooves to cooperate with the rollers; a crankshaft disposed within the rollers to drive the rollers to rotate; wherein there are one or more pump body assemblies, and when there are multiple pump body assemblies, the multiple pump body assemblies are spaced apart along the extension direction of the crankshaft; the compressor vanes are the aforementioned compressor vanes.

[0017] By applying the technical solution of this utility model, a first lubrication zone with a first recess is provided on the first side of the compressor vane near the head, and a second lubrication zone with a second recess is provided on the second side near the tail. Since the first and second lubrication zones are the most complex and wear-prone parts of the compressor vane, when lubricating oil or other lubricating media flows through the first and second recesses, a dynamic pressure effect is generated at these recesses, enhancing the oil film's load-bearing capacity. The increased oil film thickness directly reduces the solid contact between the compressor vane and the vane groove wall, effectively reducing frictional power consumption and extending the service life of the compressor vane. This solves the problem of easy wear of the vanes in existing rotary compressors, which affects compressor energy efficiency, and improves the overall operating efficiency and reliability of the compressor. Attached Figure Description

[0018] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0019] Figure 1 A schematic diagram of the structure of the compressor vane according to Embodiment 1 of the present invention after assembly with the pump body assembly and crankshaft is shown.

[0020] Figure 2 A schematic diagram of the compressor cylinder of a rolling rotor compressor according to the present invention is shown.

[0021] Figure 3 It shows Figure 1 A schematic diagram of the reaction force of the compressor vane under the vane groove support;

[0022] Figure 4 It shows Figure 1 A schematic diagram of the micropore distribution on the suction side of the compressor vane;

[0023] Figure 5 It shows Figure 1 A schematic diagram of the micropore distribution on the exhaust side of the compressor vane;

[0024] Figure 6 It shows Figure 1 A schematic diagram of the microporous dynamic pressure lubrication pressure distribution of the compressor vanes;

[0025] Figure 7 It shows Figure 1 A schematic diagram of the microporous oil-gathering effect of the compressor vanes;

[0026] Figure 8 A schematic diagram of the structure of a compressor vane according to a second embodiment of the present invention is shown;

[0027] Figure 9 A schematic diagram of the structure of a compressor vane according to a third embodiment of the present invention is shown;

[0028] Figure 10 A schematic diagram of the structure of a compressor vane according to Embodiment 4 of the present invention is shown;

[0029] Figure 11 A perspective structural schematic diagram of an embodiment of a rolling rotor compressor according to the present invention is shown.

[0030] The above figures include the following reference numerals:

[0031] 10. First side; 11. First lubrication area; 12. First recess; 121. First sub-recess; 1211. First extended recess; 1212. Second extended recess;

[0032] 20. Second side surface; 21. Second lubrication area; 22. Second recess; 221. Second sub-recess; 2211. Third extended recess; 2212. Fourth extended recess;

[0033] 30. Head;

[0034] 40. Tail;

[0035] 50. Compressor cylinder; 51. Vane groove; 52. Inlet; 53. Exhaust port; 54. Intake chamber; 55. Compression chamber;

[0036] 60. Roller; 70. Compressor vane; 80. Crankshaft; 90. Upper flange; 100. Lower flange. Detailed Implementation

[0037] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0038] It should be noted that, unless otherwise specified, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0039] In this utility model, unless otherwise stated, directional terms such as "upper" and "lower" are generally used in relation to the direction shown in the accompanying drawings, or in relation to the vertical, perpendicular, or gravitational direction; similarly, for ease of understanding and description, "left" and "right" are generally used in relation to the left and right shown in the accompanying drawings; "inner" and "outer" refer to the inner and outer contours of each component itself, but the above directional terms are not used to limit this utility model.

[0040] In order to solve the problem that the vanes of the rotary compressor are prone to wear and thus affect the compressor's energy efficiency in the prior art, this application provides a compressor vane and a rolling rotor compressor having the same.

[0041] Example 1

[0042] like Figures 1 to 5 As shown, the compressor vane has a first side 10, a second side 20 opposite to the first side 10, a head 30, and a tail 40. Both the first side 10 and the second side 20 are used to cooperate with the vane groove 51 of the compressor cylinder 50. The first side 10 is located near the air inlet 52 of the compressor cylinder 50, and the second side 20 is located near the exhaust port 53 of the compressor cylinder 50. The first side 10 has a first lubrication area 11 located near the head 30, and the first lubrication area 11 has a first recess 12 for receiving lubricating medium. The second side 20 has a second lubrication area 21 located near the tail 40, and the second lubrication area 21 has a second recess 22 for receiving lubricating medium.

[0043] By applying the technical solution of this embodiment, a first lubrication area 11 is provided on the first side 10 of the compressor vane near the head 30, and a first recess 12 is provided within the first lubrication area 11; a second lubrication area 21 is provided on the second side 20 near the tail 40, and a second recess 22 is provided within the second lubrication area 21. Since the first lubrication area 11 and the second lubrication area 21 are the parts of the compressor vane that are most subjected to complex forces and are prone to wear, when lubricating oil or other lubricating media flow through the first recess 12 and the second recess 22, a dynamic pressure effect can be generated at the recesses, enhancing the oil film bearing capacity. Due to the increase in oil film thickness, the solid contact between the compressor vane and the wall of the vane groove 51 is directly reduced, effectively reducing frictional power consumption and extending the service life of the compressor vane. This solves the problem in the prior art where the vane of a rotary compressor is prone to wear, affecting the compressor's energy efficiency, and improves the overall operating efficiency and reliability of the compressor.

[0044] In other embodiments not shown in the accompanying drawings, only the first side has a first lubrication area disposed near the head 30, the first lubrication area having a first recess for receiving lubricating medium.

[0045] In other embodiments not shown in the accompanying drawings, only the second side has a second lubrication area disposed near the tail 40, the second lubrication area having a second recess for receiving the lubricating medium.

[0046] Optionally, the first recess 12 includes a plurality of first sub-recesses 121, which are spaced apart along the length and / or height direction of the compressor vane; and / or, the second recess 22 includes a plurality of second sub-recesses 221, which are spaced apart along the length and / or height direction of the compressor vane. In this way, the above-described arrangement of the plurality of sub-recesses can generate a series of minute pressure fluctuations during the sliding of the compressor vane, similar to the principle of a micro hydraulic pump. When liquid (such as lubricating oil) flows through the sub-recesses, a localized low pressure is formed at the inlet, while a high pressure is generated at the outlet. This dynamic pressure effect helps to establish a more stable oil film, improving the oil film's load-bearing capacity, thereby reducing the direct contact between the compressor vane and the wall of the vane groove 51 and reducing friction.

[0047] In this embodiment, the first recess 12 includes a plurality of first sub-recesses 121, which are spaced apart along the length and height directions of the compressor vane. The second recess 22 includes a plurality of second sub-recesses 221, which are also spaced apart along the length and height directions of the compressor vane. By arranging the first sub-recesses 121 and second sub-recesses 221 spaced apart along the length and height directions of the compressor vane, the oil film thickness is more uniformly distributed throughout the lubrication area. This ensures good lubrication even in different parts of the compressor vane and at different operating stages, preventing localized excessive wear caused by variations in oil film thickness. Simultaneously, the small dynamic pressure effect generated by the multiple sub-recesses increases the oil film bearing capacity, reducing direct friction between the compressor vane and the vane groove, thereby lowering the power consumption on both sides of the compressor vane.

[0048] Optionally, the first sub-recess 121 is at least one of a groove, a blind hole, and a through hole; and / or, the second sub-recess 221 is at least one of a groove, a blind hole, and a through hole. Thus, regardless of whether it is a groove, a blind hole, or a through hole, the above-described configuration of the sub-recesses can effectively store lubricating oil. During the movement of the compressor vanes, the lubricating oil is squeezed, penetrated, or carried to the contact area between the first side surface 10 and the second side surface 20 and the vane groove 51, forming an oil film. This significantly enhances lubrication performance, reduces friction between the vane and the vane groove, and lowers frictional power consumption. Simultaneously, the above configuration allows for more flexible selection of the shape of the first sub-recess 121 and / or the second sub-recess 221 to meet different usage requirements and operating conditions, and also reduces the processing flexibility required of operators.

[0049] In this embodiment, both the first sub-recess 121 and the second sub-recess 221 are grooves.

[0050] Optionally, the total area s1 of the first recess 12 and the total area S1 of the first lubrication area 11 satisfy the following condition: 0.05S1≤s1≤0.3S1; and / or, the total area s2 of the second recess 22 and the total area S2 of the second lubrication area 21 satisfy the following condition: 0.05S2≤s2≤0.3S2. Thus, if the total area of ​​the recesses is too small, it will not be sufficient to generate an effective dynamic pressure effect, while if it is too large, it may lead to a decrease in oil film bearing capacity, affecting the lubrication effect. By setting a reasonable range for the total area of ​​the recesses, sufficient oil film thickness and dynamic pressure effect can be ensured, thereby establishing an effective lubrication layer between the compressor vane and the wall of the vane groove 51, reducing direct solid contact and lowering frictional power consumption. Simultaneously, the compressor vane not only bears frictional force during compressor operation but also undertakes heat dissipation tasks. Its low thermal diffusivity makes it more effective in suppressing heat transfer from the compression side to the suction side, ensuring sufficient lubricating oil storage space while preventing excessive material removal from affecting the structural rigidity and insulation effect of the compressor vane.

[0051] Alternatively, the compressor vanes may be made of ceramic material.

[0052] Optionally, the compressor vanes are made of zirconium oxide.

[0053] Optionally, all first sub-recesses 121 may be a single hole type or a combination of multiple hole types.

[0054] Optionally, the depth d1 of the first recess 12 is greater than or equal to 5 μm and less than or equal to 100 μm; and / or, the depth d1 of the second recess 22 is greater than or equal to 5 μm and less than or equal to 100 μm. Thus, setting the depths of the first recess 12 and the second recess 22 to between 5 μm and 100 μm allows for more efficient utilization of lubricating oil when the compressor vane contacts the wall of the vane groove 51. As the compressor vane reciprocates within the compressor cylinder 50, the lubricating oil can be captured and retained within these micropores or recesses. With the movement of the compressor vane, this lubricating oil is carried into the contact area between the compressor vane and the groove wall of the vane groove 51 to form an oil film. Meanwhile, by setting the depth of the first recess 12 and the second recess 22 between 5μm and 100μm, not only is the feasibility of processing taken into account (too small a depth may not form an effective dynamic pressure effect, and too large a depth may affect the structural strength and processing efficiency of the slide), but also the micropores are ensured to continue to play a role in the entire working cycle of the slide, so as not to lose effectiveness quickly due to wear.

[0055] In this embodiment, the first boundary of the first lubrication area 11 and the head 30 have a first distance y1, and the second boundary of the first lubrication area 11 and the head 30 have a second distance y2. The first distance y1 and the second distance y2 satisfy:

[0056]

[0057] 2e≤y2≤L2;

[0058] Where R is the inner diameter of compressor cylinder 50, r is the outer diameter of the roller, and e is the eccentricity of the compressor. If the support reaction force at the first side 10 is less than the support reaction force at the second side 20, the range of the compressor crankshaft angle is α1≤θ≤α2. When the support reaction force at the first side 10 is greater than the support reaction force at the second side 20, the range of the compressor crankshaft angle is α2<θ≤α3. h L1 is the radius of the arc of the head 30, and L2 is the length of the slider groove 51.

[0059] It should be noted that y1, y2, e, r, R, R h The units for L1 and L2 are mm, and the units for α1, α2, α3 and θ are rad.

[0060] It should be noted that the crankshaft angle of the compressor refers to the angle of rotation of the eccentric part of the crankshaft relative to its initial position, that is, the angle between the line connecting the central axis of the eccentric part and the central axis of the crankshaft and the initial position.

[0061] Specifically, ignoring the clearance value, e = Rr, and the length of the compressor vane extending into the compressor cylinder 50 is x, approximately... Therefore, the maximum extension of the compressor vane is x = 2e.

[0062] like Figure 3 As shown, the compressor vane is prone to tilting when subjected to unbalanced gas forces on both sides. Within a certain range, the head 30 tilts towards the intake side and the tail 40 tilts towards the exhaust side. The vane groove 51 provides a reaction force F to the intake side. x1 The reaction force F on the exhaust side support x2 .

[0063] In this embodiment, there is a third distance y3 between the first boundary of the second lubrication area 21 and the tail 40, and a fourth distance y4 between the second boundary of the second lubrication area 21 and the tail 40. The third distance y3 and the fourth distance y4 satisfy the following:

[0064]

[0065] like Then y3≥0 is satisfied; L1 is the length of the compressor vane.

[0066] It should be noted that the units for y3, y4, and L1 are mm.

[0067] Optionally, each first sub-recess 121 is a circular hole; or, the plurality of first sub-recesses 121 include first sub-recess groups spaced apart along the length direction of the compressor vane, each first sub-recess group including a plurality of first extension recesses 1211 and a plurality of second extension recesses 1212 spaced apart or connected sequentially along the height direction of the compressor vane, a second extension recess 1212 is provided between each two adjacent first extension recesses 1211, and a first extension recess 1211 is provided between each two adjacent second extension recesses 1212; the sliding direction of the compressor vane is set at a first angle with the extension direction of each first extension recess 1211 and the extension direction of each second extension recess 1212, and the extension direction of the first extension recess 1211 is set at a second angle with the extension direction of the second extension recess 1212. Thus, when each of the first sub-recesses 121 is a circular hole, the uniform distribution of the micropores can promote the formation of a stable oil film between the compressor vane and the vane groove 51. Due to its non-directional nature, the circular hole can maintain good oil film bearing capacity regardless of the movement of the compressor vane. When the multiple first sub-recesses 121 include a group of first sub-recesses spaced along the length of the compressor vane and a second extended recess 1212 between every two adjacent first extended recesses 1211, and a first extended recess 1211 between every two adjacent second extended recesses 1212, this design forms alternating extended recesses. The first extended recesses 1211 and the second extended recesses 1212 are arranged at a specific angle and in a specific pattern, which can generate more complex hydrodynamic effects when the compressor vane slides. When the compressor vane moves, the lubricating oil will form a local dynamic pressure effect in these alternating recesses, further enhancing the oil film's bearing capacity and stability, thereby significantly reducing direct friction and wear between solids.

[0068] In this embodiment, the plurality of first sub-recesses 121 include first sub-recess groups spaced apart along the length direction of the compressor vane. Each first sub-recess group includes a plurality of first extending recesses 1211 and a plurality of second extending recesses 1212 spaced apart along the height direction of the compressor vane. A second extending recess 1212 is provided between every two adjacent first extending recesses 1211, and a first extending recess 1211 is provided between every two adjacent second extending recesses 1212. The sliding direction of the compressor vane is set at a first angle with the extending direction of each first extending recess 1211 and the extending direction of each second extending recess 1212, and the extending direction of the first extending recess 1211 is set at a second angle with the extending direction of the second extending recess 1212.

[0069] Optionally, each second sub-recess 221 is a circular hole; or, the plurality of second sub-recesses 221 include a group of second sub-recesses spaced apart along the length direction of the compressor vane, each group of second sub-recesses including a plurality of third extending recesses 2211 and a plurality of fourth extending recesses 2212 spaced apart or connected sequentially along the height direction of the compressor vane, a fourth extending recess 2212 is provided between each two adjacent third extending recesses 2211, and a third extending recess 2211 is provided between each two adjacent fourth extending recesses 2212; the sliding direction of the compressor vane is set at a third angle with the extending direction of each third extending recess 2211 and the extending direction of each fourth extending recess 2212, and the extending direction of the third extending recess 2211 is set at a fourth angle with the extending direction of the fourth extending recess 2212. Thus, when each of the second sub-recesses 221 is a circular hole, the uniform distribution of the micropores can promote the formation of a stable oil film between the compressor vane and the vane groove 51. Due to its non-directional nature, the circular hole can maintain a good oil film bearing capacity regardless of how the compressor vane moves. When the multiple second sub-recesses 221 include a group of second sub-recesses spaced apart along the length direction of the compressor vane, and each group of second sub-recesses includes multiple third extension recesses 2211 and multiple fourth extension recesses 2212 spaced apart or connected sequentially along the height direction of the compressor vane, with a fourth extension recess 2212 between each two adjacent third extension recesses 2211 and a third extension recess 2211 between each two adjacent fourth extension recesses 2212, this design forms alternating extension recesses. The third extension recesses 2211 and the fourth extension recesses 2212 are arranged at a specific angle and in a specific arrangement, which can generate more complex hydrodynamic effects when the compressor vane slides. When the compressor vanes move, the lubricating oil creates a local dynamic pressure effect in these alternating recesses, further enhancing the oil film's load-bearing capacity and stability, thereby significantly reducing direct friction and wear between solids.

[0070] In this embodiment, the plurality of second sub-recesses 221 include groups of second sub-recesses spaced apart along the length direction of the compressor vane. Each group of second sub-recesses includes a plurality of third extending recesses 2211 and a plurality of fourth extending recesses 2212 spaced apart along the height direction of the compressor vane. A fourth extending recess 2212 is provided between every two adjacent third extending recesses 2211, and a third extending recess 2211 is provided between every two adjacent fourth extending recesses 2212. The sliding direction of the compressor vane is set at a third angle with the extending direction of each third extending recess 2211 and the extending direction of each fourth extending recess 2212, and the extending direction of the third extending recess 2211 is set at a fourth angle with the extending direction of the fourth extending recess 2212.

[0071] Optionally, the compressor vanes are made of an insulating material.

[0072] Alternatively, the compressor vanes may be made of zirconium oxide or aluminum oxide.

[0073] like Figure 9 As shown, when lubricating oil flows through the micropores, the pressure first decreases and then increases. Since the pressure decreases until the cavitation pressure stops changing, the decrease is less than the increase, so the overall load-bearing capacity of the oil film increases.

[0074] like Figure 7 As shown, the compressor vanes move in opposite directions when extending and retracting, and the shear flow of the lubricating oil also flows in opposite directions. When the compressor vanes extend, as... Figure 7 As shown in (a), the pressure is higher near the tail 40 and lower near the head 30 between the two rows of micro-holes. Laterally, the pressure is higher near the outer edge and lower near the inner edge, forcing the lubricating oil to converge towards the center, increasing the central pressure and thus enhancing the load-bearing capacity. Similarly, when the compressor vanes retract, as... Figure 7 As shown in (b), the pressure is higher near the head 30 and lower near the tail 40. In a horizontal view, the pressure is higher near the outer side and lower near the inner side, which forces the lubricating oil to converge towards the middle, increasing the middle pressure and thus improving the load-bearing capacity.

[0075] like Figure 11 As shown, this application also provides a rolling rotor compressor, including a pump body assembly and a crankshaft 80. The pump body assembly includes a compressor cylinder 50, rollers 60, and compressor vanes 70. The rollers 60 are rotatably disposed within the compressor cylinder 50, which has a vane groove 51. The compressor vanes 70 are slidably disposed within the vane groove 51 to cooperate with the rollers 60. The crankshaft 80 passes through the rollers 60 to drive the rollers 60 to rotate. The pump body assembly may be one or more; when there are multiple pump body assemblies, they are spaced apart along the extension direction of the crankshaft 80. The compressor vanes 70 are the aforementioned compressor vanes.

[0076] Specifically, the compressor cylinder 50, rollers 60, and primary compressor vane 70 divide the working volume into an intake chamber 54 and a compression chamber 55. When the pressure in the compression chamber 55 reaches the exhaust pressure, the valve at the exhaust port 53 opens, and the gas is discharged. The side of the vane closest to the intake port 52 is called the intake side, and the side closest to the exhaust port 53 is called the exhaust side. The end that contacts the outer cylindrical surface of the roller 60 is called the head 30, and the other end is called the tail 40.

[0077] like Figure 11As shown, the rolling rotor compressor also includes an upper flange 90 and a lower flange 100. The compressor cylinder 50, the upper flange 90, and the lower flange 100 surround each other to form a working cavity. As the motor drives the crankshaft 80 to rotate the roller 60, the volume of the suction chamber 54 and the compression chamber 55 separated by the compressor vanes 70 and the roller 60 changes periodically to complete the suction and exhaust process.

[0078] Example 2

[0079] The difference between the compressor vane in Embodiment 2 and Embodiment 1 is that the shapes of the first recess 12 and the second recess 22 are different.

[0080] like Figure 8 As shown, a plurality of first sub-recesses 121 include first sub-recess groups spaced apart along the length direction of the compressor vane. Each first sub-recess group includes a plurality of first extending recesses 1211 and a plurality of second extending recesses 1212 connected sequentially along the height direction of the compressor vane. A second extending recess 1212 is provided between every two adjacent first extending recesses 1211, and a first extending recess 1211 is provided between every two adjacent second extending recesses 1212. The sliding direction of the compressor vane is set at a first angle with the extending direction of each first extending recess 1211 and the extending direction of each second extending recess 1212, and the extending direction of the first extending recess 1211 is set at a second angle with the extending direction of the second extending recess 1212.

[0081] Specifically, the above-described configuration forms alternating extended recesses, wherein the first extended recess 1211 and the second extended recess 1212 are arranged at a specific angle and in a specific pattern, which can generate more complex hydrodynamic effects when the compressor vanes slide. When the compressor vanes move, the lubricating oil forms a localized hydrodynamic pressure effect in these alternating recesses, further enhancing the oil film's load-bearing capacity and stability, thereby significantly reducing direct friction and wear between solids.

[0082] like Figure 8 As shown, the plurality of second sub-recesses 221 include groups of second sub-recesses spaced apart along the length direction of the compressor vane. Each group of second sub-recesses includes a plurality of third extending recesses 2211 and a plurality of fourth extending recesses 2212 connected sequentially along the height direction of the compressor vane. A fourth extending recess 2212 is provided between every two adjacent third extending recesses 2211, and a third extending recess 2211 is provided between every two adjacent fourth extending recesses 2212. The sliding direction of the compressor vane is set at a third angle with the extending direction of each third extending recess 2211 and the extending direction of each fourth extending recess 2212, and the extending direction of the third extending recess 2211 is set at a fourth angle with the extending direction of the fourth extending recess 2212.

[0083] Specifically, the above arrangement forms alternating extended recesses, wherein the third extended recess 2211 and the fourth extended recess 2212 are arranged at specific angles and in a specific pattern, which can generate more complex hydrodynamic effects when the compressor vanes slide. When the compressor vanes move, the lubricating oil forms a localized dynamic pressure effect in these alternating recesses, further enhancing the oil film's load-bearing capacity and stability, thereby significantly reducing direct friction and wear between solids.

[0084] Example 3

[0085] The compressor vane in Embodiment 3 differs from that in Embodiment 1 in that the shapes of the first recess 12 and the second recess 22 are different.

[0086] like Figure 9 As shown, each of the first sub-recesses 121 is a circular hole. The uniform distribution of micropores can promote the formation of a stable oil film between the compressor vane and the vane groove 51. Due to its non-directional characteristics, the circular hole can maintain a good oil film bearing capacity no matter how the compressor vane moves.

[0087] like Figure 9 As shown, each second sub-recess 221 is a round hole. The uniform distribution of micropores can promote the formation of a stable oil film between the compressor vane and the vane groove 51. Due to its non-directional characteristics, the round hole can maintain a good oil film bearing capacity no matter how the compressor vane moves.

[0088] Example 4

[0089] The compressor vane in Embodiment 4 differs from that in Embodiment 3 in that the shapes of the first recess 12 and the second recess 22 are different.

[0090] like Figure 10 As shown, each of the first sub-recesses 121 is an elliptical hole, which can generate more complex hydrodynamic effects when the compressor vanes slide. Specifically, when the compressor vanes move, the lubricating oil will form a local dynamic pressure effect in these alternating recesses, further enhancing the load-bearing capacity and stability of the oil film, thereby significantly reducing direct friction and wear between solids.

[0091] like Figure 10 As shown, each of the second sub-recesses 221 is an elliptical hole, which can generate more complex hydrodynamic effects when the compressor vanes slide. Specifically, when the compressor vanes move, the lubricating oil will form a local dynamic pressure effect in these alternating recesses, further enhancing the load-bearing capacity and stability of the oil film, thereby significantly reducing direct friction and wear between solids.

[0092] As can be seen from the above description, the embodiments of this utility model achieve the following technical effects:

[0093] By setting a first lubrication zone near the head of the compressor vane and a first recess within the first lubrication zone, and setting a second lubrication zone near the tail of the second side and a second recess within the second lubrication zone, the first and second lubrication zones are the most complex and wear-prone parts of the compressor vane. When lubricating oil or other lubricating media flows through the first and second recesses, a dynamic pressure effect is generated at the recesses, enhancing the oil film's load-bearing capacity. The increased oil film thickness directly reduces the solid contact between the compressor vane and the vane groove wall, effectively reducing frictional power consumption and extending the service life of the compressor vane. This solves the problem of easy wear of the vanes in existing rotary compressors, which affects compressor energy efficiency, and improves the overall operating efficiency and reliability of the compressor.

[0094] Obviously, the embodiments described above are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort should fall within the protection scope of this utility model.

[0095] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0096] It should be noted that the terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in sequences other than those illustrated or described herein.

[0097] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor vane, characterized in that, The compressor vane has a first side (10), a second side (20) opposite to the first side (10), a head (30), and a tail (40). The first side (10) and the second side (20) are both used to cooperate with the vane groove (51) of the compressor cylinder (50). The first side (10) is located near the air inlet (52) of the compressor cylinder (50), and the second side (20) is located near the exhaust port (53) of the compressor cylinder (50). The first side (10) has a first lubrication area (11) located near the head (30), and the first lubrication area (11) has a first recess (12) for receiving lubricating medium. And / or, the second side (20) has a second lubrication area (21) located near the tail (40), and the second lubrication area (21) has a second recess (22) for receiving lubricating medium.

2. The compressor vane according to claim 1, characterized in that, The first recess (12) includes a plurality of first sub-recesses (121), which are spaced apart along the length and / or height direction of the compressor vane; and / or, The second recess (22) includes a plurality of second sub-recesses (221), which are spaced apart along the length and / or height of the compressor vane.

3. The compressor vane according to claim 2, characterized in that, The first sub-recess (121) is at least one of a groove, a blind hole, and a through hole; and / or, the second sub-recess (221) is at least one of a groove, a blind hole, and a through hole.

4. The compressor vane according to claim 1, characterized in that, The total area s1 of the first recess (12) and the total area S1 of the first lubrication area (11) satisfy the following condition: 0.05S1≤s1≤0.3S1; and / or, the total area s2 of the second recess (22) and the total area S2 of the second lubrication area (21) satisfy the following condition: 0.05S2≤s2≤0.3S2.

5. The compressor vane according to claim 1, characterized in that, The depth d1 of the first recess (12) is greater than or equal to 5 μm and less than or equal to 100 μm; and / or the depth d1 of the second recess (22) is greater than or equal to 5 μm and less than or equal to 100 μm.

6. The compressor vane according to claim 1, characterized in that, The first boundary of the first lubrication area (11) has a first distance y1 between it and the head (30), and the second boundary of the first lubrication area (11) has a second distance y2 between it and the head (30). The first distance y1 and the second distance y2 satisfy: 2e≤y2≤L2; Where R is the inner diameter of the compressor cylinder (50), r is the outer diameter of the roller, and e is the eccentricity of the compressor. If the support reaction force at the first side (10) is less than the support reaction force at the second side (20), the crankshaft angle of the compressor is in the range of α1≤θ≤α2. When the support reaction force at the first side (10) is greater than the support reaction force at the second side (20), the crankshaft angle of the compressor is in the range of α2<θ≤α3. h L1 is the radius of the arc of the head (30), and L2 is the length of the sliding groove (51).

7. The compressor vane according to claim 1, characterized in that, The second lubrication zone (21) has a third distance y3 between its first boundary and the tail (40), and the second boundary of the second lubrication zone (21) has a fourth distance y4 between its second boundary and the tail (40). The third distance y3 and the fourth distance y4 satisfy the following: like Then y3≥0 is satisfied; L1 is the length of the compressor vane.

8. The compressor vane according to claim 2, characterized in that, Each of the first sub-recesses (121) is a circular hole; or, The plurality of first sub-recesses (121) include first sub-recesses grouped at intervals along the length direction of the compressor vane. Each first sub-recesse group includes a plurality of first extension recesses (1211) and a plurality of second extension recesses (1212) spaced at intervals or connected sequentially along the height direction of the compressor vane. A second extension recess (1212) is provided between every two adjacent first extension recesses (1211), and a first extension recess (1211) is provided between every two adjacent second extension recesses (1212). The sliding direction of the compressor vane is set at a first angle with the extension direction of each first extension recess (1211) and the extension direction of each second extension recess (1212), and the extension direction of the first extension recess (1211) is set at a second angle with the extension direction of the second extension recess (1212).

9. The compressor vane according to claim 2, characterized in that, Each of the second sub-recesses (221) is a circular hole; or, The plurality of second sub-recesses (221) include groups of second sub-recesses spaced apart along the length direction of the compressor vane. Each group of second sub-recesses includes a plurality of third extension recesses (2211) and a plurality of fourth extension recesses (2212) spaced apart or connected sequentially along the height direction of the compressor vane. A fourth extension recess (2212) is provided between every two adjacent third extension recesses (2211), and a third extension recess (2211) is provided between every two adjacent fourth extension recesses (2212). The sliding direction of the compressor vane is set at a third angle with the extension direction of each third extension recess (2211) and the extension direction of each fourth extension recess (2212). The extension direction of the third extension recess (2211) is set at a fourth angle with the extension direction of the fourth extension recess (2212).

10. The compressor vane according to claim 1, characterized in that, The compressor vanes are made of heat-insulating material.

11. A rolling rotor compressor, characterized in that, include: The pump body assembly includes a compressor cylinder (50), a roller (60), and a compressor vane (70). The roller (60) is rotatably disposed within the compressor cylinder (50). The compressor cylinder (50) has a vane groove (51). The compressor vane (70) is slidably disposed within the vane groove (51) to cooperate with the roller (60). A crankshaft (80) is inserted inside the roller (60) to drive the roller (60) to rotate; The pump body assembly is one or more, and when there are multiple pump body assemblies, the multiple pump body assemblies are spaced apart along the extension direction of the crankshaft (80); the compressor vane (70) is the compressor vane of any one of claims 1 to 10.

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