Roller ring for rotor compressor, compressor, air conditioner

Abstract

The present invention discloses a roller ring for a rotary compressor, a compressor, and an air conditioner. The roller ring comprises: an annular sleeve and an annular thrust portion, wherein the annular sleeve and the annular thrust portion are cooperatively sleeved on the upper or lower portion of the eccentric portion; the annular sleeve has a sidewall defining a sleeve space for sleeved eccentric portion; the annular thrust portion is disposed at one end of the annular sleeve and is used to thrust the top or bottom of the eccentric portion to limit the eccentric portion in its axial direction; the annular thrust portion is provided with a through hole through which the crankshaft shaft passes so that the annular thrust portion thrusts the eccentric portion; the inner wall of the annular sleeve is provided with a first friction-reducing structure for reducing friction between the annular sleeve and the eccentric portion; and / or the inner wall of the thrust eccentric portion of the annular thrust portion is provided with a second friction-reducing structure for reducing friction between the annular thrust portion and the eccentric portion. The compressor employing the roller ring improves operational stability.

Description

Technical Field

[0001] The present invention relates to the technical field related to compressors, and in particular to a roller ring for a rotor compressor, a compressor, and an air conditioner. Background Art

[0002] Currently, rotary compressors consist of a power unit that drives the refrigerant and a compression unit that converts the refrigerant into high-pressure gas. These two components are connected by an interference fit between the crankshaft and the motor rotor to transmit mechanical energy. The rotation of the motor rotor drives the rollers in the cylinder, which, in conjunction with the vanes, enable the operation of the rotary compressor. The axial restraint of the rotary compressor's crankshaft is achieved by the fit between the lower thrust surface of the crankshaft's eccentric portion and the end face of the lower flange bearing. However, in actual operation, the crankshaft's eccentric portion is prone to deformation under the action of gas and eccentric forces. The axial restraint of the crankshaft is highly unstable due to the action of the thrust surface of the crankshaft's eccentric portion, resulting in low reliability during compressor operation.

[0003] For example, the existing method employs an eccentric portion and a thrust portion provided on the rotating shaft body, with the eccentric portion and the thrust portion spaced apart in the axial direction of the rotating shaft body. By providing a separate thrust portion with a thrust function, separated from the eccentric portion, the eccentric portion no longer functions as a thrust portion, thereby preventing wear of the eccentric portion during operation and increasing the service life of the rotating shaft. However, this method places high demands on the strength of the crankshaft. As a component rotating at high speed during compressor operation, the crankshaft is easily damaged. Furthermore, the maximum outer diameter of the thrust surface that axially constrains the crankshaft in the existing technology is small, resulting in poor crankshaft stability and reduced reliability during compressor operation. Summary of the Invention

[0004] In view of this, the present invention discloses a roller ring for a rotor compressor, a compressor, and an air conditioner, which are used to at least solve the problem of low reliability caused by unstable axial constraint of the existing crankshaft.

[0005] In order to achieve the above-mentioned objectives, the present invention adopts the following technical solutions:

[0006] A first aspect of the present invention discloses a roller ring for a rotary compressor, wherein the rotary compressor has a crankshaft, an eccentric portion is provided on the shaft of the crankshaft, and the roller ring comprises: an annular sleeve and an annular thrust portion, wherein the annular sleeve and the annular thrust portion are fitted together and sleeved on the upper or lower portion of the eccentric portion;

[0007] The side wall of the annular sleeve forms a sleeve space for sleeve-mounting the eccentric portion;

[0008] The annular thrust portion is provided at one end of the annular sleeve and is used to push the top or bottom of the eccentric portion to limit the eccentric portion in its axial direction; the annular thrust portion is provided with a through hole, and the through hole is used for the shaft of the crankshaft to pass through so that the annular thrust portion pushes the eccentric portion;

[0009] The inner wall of the annular sleeve is provided with a first friction-reducing structure, which is used to reduce the friction between the annular sleeve and the eccentric part; and / or the inner wall of the eccentric part of the annular thrust part is provided with a second friction-reducing structure, which is used to reduce the friction between the annular thrust part and the eccentric part.

[0010] Further optionally, the first friction reducing structure includes: a first groove provided on the inner wall of the annular sleeve, the first groove being used for storing lubricating oil or being equipped with balls.

[0011] Further optionally, the first groove is a circumferential sliding groove opened on the inner wall of the annular sleeve in the circumferential direction of the annular sleeve.

[0012] Further optionally, the first groove is a plurality of microporous grooves evenly distributed on the inner wall of the annular sleeve.

[0013] Further optionally, the second friction reducing structure includes: a second groove provided on the inner wall of the annular thrust portion that pushes the eccentric portion, the second groove being used for storing lubricating oil or accommodating balls.

[0014] Further optionally, the second groove is an annular groove opened on the inner wall of the annular thrust portion that stops the eccentric portion from pushing.

[0015] Further optionally, the second grooves are a plurality of micro-hole grooves opened on the inner wall of the annular thrust portion that stops the eccentric portion from thrusting.

[0016] Further optionally, the roller ring is coaxially arranged with the eccentric portion, and the through hole is located at the center of the annular thrust portion, wherein the aperture of the through hole is larger than the diameter of the crankshaft, and the aperture of the through hole is smaller than the diameter of the eccentric portion.

[0017] A second aspect of the present invention discloses a compressor, comprising: at least one roller ring as described above.

[0018] Further optionally, there are two roller rings, and the compressor further comprises:

[0019] Cylinder and the slide inside it;

[0020] A crankshaft, the crankshaft being passed through the cylinder, and the crankshaft shaft being provided with an eccentric portion cooperating with the slide, the eccentric portion being located in the cylinder; wherein the two roller rings are respectively sleeved on the upper and lower portions of the eccentric portion to prevent the crankshaft from thrusting in the axial direction of the eccentric portion;

[0021] a first flange bearing, sleeved on the crankshaft, for limiting the position of the roller ring on the upper part of the eccentric part in the axial direction on the upper part of the crankshaft;

[0022] The second flange bearing is sleeved on the crankshaft and is used to limit the roller ring at the lower part of the eccentric part in the axial direction at the lower part of the crankshaft.

[0023] A third aspect of the present invention discloses an air conditioner, comprising the compressor as described above.

[0024] Beneficial effects: The present invention provides a roller ring as a thrust roller to protect the crankshaft in the compressor and improve its reliability. The roller ring is symmetrically installed along the axial direction of the eccentric portion of the crankshaft. The roller ring increases the maximum outer diameter of the crankshaft thrust surface, improves the stability of the axial constraint of the crankshaft, and is beneficial to the smooth operation of the compressor. The roller ring is two L-shaped radial cross-section rings assembled on the upper and lower end faces of the eccentric portion. During operation, both roller rings can rotate (produce relative rotation), which is beneficial to the uniformity of the relative sliding between the crankshaft and the roller. The inner wall of the roller ring has a friction-reducing structure, which produces elastic deformation after the eccentric portion is deformed, reducing mutual wear between components. In addition, when the inner wall of the roller ring adopts an annular groove, it helps the flow of lubricating oil, promotes lubrication between the crankshaft and the roller, and reduces wear. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The above and other objects, features, and advantages of the present invention will become more apparent by describing in detail exemplary embodiments thereof with reference to the accompanying drawings. The drawings described below are only some embodiments disclosed in the present invention. It is obvious to a person skilled in the art that other drawings can be derived from these drawings without inventive effort.

[0026] Figure 1 A cross-sectional view of a compressor body according to an embodiment is shown;

[0027] Figure 2 An exploded view of a thrust roller and a crankshaft according to an embodiment is shown;

[0028] Figure 3 A partial cross-sectional view of a thrust roller and a crankshaft according to an embodiment is shown;

[0029] Figure 4 An exploded view of a thrust roller according to an embodiment is shown;

[0030] Figure 5 A cross-sectional view of a thrust roller and a crankshaft according to an embodiment is shown;

[0031] Figure 6 A cross-sectional view of a thrust roller according to an embodiment is shown;

[0032] Figure 7 A cross-sectional view of a roller ring according to an embodiment is shown;

[0033] Figure 8 A partial cross-sectional view of a crankshaft according to an embodiment is shown;

[0034] Figure 9 A cross-sectional view of a cylinder body according to an embodiment is shown;

[0035] Figure 10 A cross-sectional view of a second flange bearing according to an embodiment is shown;

[0036] Figure 11 A schematic diagram of a roller ring provided with micro-porous grooves according to an embodiment is shown;

[0037] Figure 12 A schematic diagram of a roller ring with balls arranged thereon is shown in one embodiment.

[0038] In the figure: 1. Crankshaft; 11. Eccentric part; 2. First flange bearing; 3. Thrust roller; 301. Circular thrust part; 302. Circular sleeve; 31. Roller ring; 311. Second groove; 312. First groove; 313. Microporous groove; 314. Ball; 4. Second flange bearing; 5. Sliding vane; 6. Cylinder. DETAILED DESCRIPTION

[0039] To make the objectives, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts shall fall within the scope of protection of the present invention.

[0040] The terms used in the embodiments of the present invention are for the purpose of describing specific embodiments only and are not intended to limit the present invention. The singular forms "a," "the," and "the" used in the embodiments of the present invention and the appended claims are also intended to include plural forms, unless the context clearly indicates otherwise. "A plurality" generally includes at least two, but does not exclude the inclusion of at least one.

[0041] It should be understood that the term "and / or" as used herein is merely a description of the relationship between associated objects, indicating that three possible relationships exist. For example, "A and / or B" can represent: A exists alone, A and B exist simultaneously, or B exists alone. Furthermore, the character " / " in this document generally indicates that the associated objects are in an "or" relationship.

[0042] It should also be noted that the terms "include," "comprises," or any other variations thereof are intended to encompass non-exclusive inclusion, such that a product or system comprising a series of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such product or system. In the absence of further limitations, an element defined by the phrase "comprises a..." does not exclude the presence of other identical elements in the product or system comprising the element.

[0043] Currently, compressors face problems with poor operating stability. For example, when the motor rotor drives the crankshaft to rotate at high speed, the crankshaft relies on the thrust surface of the eccentric part to limit axial displacement, resulting in poor operating stability due to the small thrust surface. There is also uneven sliding friction between the crankshaft or vanes and the rollers, and the rollers do not rotate, causing excessive wear and damage to parts. The high-speed rotation of the rotor compressor causes the crankshaft to deform under load, resulting in contact wear between the crankshaft, rollers, and bearings, which in turn causes friction and reduces mechanical efficiency. Furthermore, the lubrication conditions between the crankshaft and rollers are relatively poor, resulting in easy wear between components and low compressor reliability. To improve the poor crankshaft stability of existing rotary compressors, which relies on the contact between the thrust surface of the crankshaft's eccentric portion and the lower flange bearing for axial constraint, the present invention proposes a rotary compressor and its thrust roller. The rollers are two roller rings with an overall L-shaped radial cross-section, assembled axially symmetrically at the upper and lower ends of the crankshaft's eccentric portion. The crankshaft's deadweight acts on the lower roller ring, which is mounted on the lower end face of the eccentric portion. The lower end face of the lower roller ring cooperates with the lower flange bearing to achieve axial constraint on the crankshaft. This compressor utilizes the thrust surface of the roller ring to limit the axial displacement of the crankshaft. Due to the large maximum outer diameter of the thrust surface, the crankshaft's axial support is better, thereby improving the stability of the crankshaft's operation. When the thrust roller adopts two roller rings arranged one above the other, there is no radial constraint between the two rings, which is conducive to the self-rotation of the two rings. It can effectively solve the problem of uneven sliding friction between the vane or crankshaft and the roller, causing excessive wear and damage to parts. At the same time, the annular groove on the inner wall of the roller can improve the lubrication effect between the crankshaft and the roller, and increase the elastic deformation of the eccentric part of the crankshaft after deformation, further reducing the friction and wear caused by deformation.

[0044] To further illustrate the technical solution of the present invention, Figures 1-12As shown, the following specific embodiments are provided.

[0045] Example 1

[0046] In this embodiment, a roller ring 31 for a rotary compressor is provided. It should be noted that the rotary compressor comprises a crankshaft 1, the shaft of which is provided with an eccentric portion 11. The roller ring 31 in this embodiment comprises an annular sleeve 302 and an annular thrust portion 301. The annular sleeve 302 and the annular thrust portion 301 are fitted over or under the eccentric portion 11.

[0047] Specifically, the sidewall of the annular sleeve forms a space for the eccentric portion 11 to be sleeved thereon. The annular thrust portion is provided at one end of the annular sleeve and is used to push against the top or bottom of the eccentric portion 11 to limit the eccentric portion 11 in its axial direction. The annular thrust portion is provided with a through hole through which the shaft of the crankshaft 1 is passed so that the annular thrust portion can push against the eccentric portion 11.

[0048] In order to reduce the friction between the roller ring 31 and the eccentric part 11, a first friction-reducing structure is provided on the inner wall of the annular sleeve, and the first friction-reducing structure is used to reduce the friction between the annular sleeve and the circumferential surface of the eccentric part 11; and / or, a second friction-reducing structure is provided on the inner wall of the thrust eccentric part 11 of the annular thrust part, and the second friction-reducing structure is used to reduce the friction between the annular thrust part and the top or bottom of the eccentric part 11.

[0049] Preferably, the first friction-reducing structure includes: a first groove 312 provided on the inner wall of the annular sleeve, the first groove 312 being used to store lubricating oil or being equipped with balls 314. Furthermore, the first groove 312 is a circumferential groove provided on the inner wall of the annular sleeve in the circumferential direction of the annular sleeve. The number of circumferential grooves is multiple, preferably 3-8. Based on the roller ring 31 of the friction-reducing structure, when the weight of the crankshaft 1 acts on the inner wall of the roller ring 31, the roller ring 31 cooperates with the end face of the lower flange to complete the axial constraint of the crankshaft 1 and achieve stable rotation of the crankshaft 1; since the inner wall of the roller ring 31 has a circumferential groove, when the compressor is running, the eccentric part 11 is deformed, and the circumferential groove produces elastic deformation, reducing the mutual influence between the components, and the lubricating oil can enter the contact surface through the circumferential groove to improve the lubrication effect.

[0050] In another alternative, the first groove 312 is a plurality of microporous grooves 313 evenly distributed on the inner wall of the annular sleeve. These microporous grooves 313 can store a certain amount of lubricating oil, thereby reducing friction between the annular sleeve and the eccentric portion 11. Furthermore, compared to a friction-reducing structure using circumferential grooves, this approach can improve the structural strength of the annular sleeve.

[0051] Similarly, in this embodiment, the second friction-reducing structure includes: a second groove 311 provided on the inner wall of the thrust eccentric portion 11 of the annular thrust portion, the second groove 311 being used to store lubricating oil or to be equipped with balls 314. Furthermore, the second groove 311 is an annular groove provided on the inner wall of the thrust eccentric portion 11 of the annular thrust portion. There are also multiple annular grooves, and the number can be set according to the size of the annular thrust portion. Preferably, the number of annular grooves is 3-5. By storing a certain amount of lubricating oil in the annular groove provided on the annular thrust portion, the friction force caused by the annular thrust portion on the eccentric portion 11 during rotation can be reduced. Alternatively, the second groove 311 is a plurality of microporous grooves 313 provided on the inner wall of the thrust eccentric portion 11 of the annular thrust portion.

[0052] It should be noted that balls 314 may also be provided in the first groove 312 and / or the second groove 311 to convert the sliding friction between the roller ring 31 and the eccentric portion 11 of the crankshaft 1 into rolling friction, and the diameter of the balls 314 is equal to the groove width.

[0053] In this embodiment, the roller ring 31 and the eccentric portion 11 are coaxial after assembly, and the through hole on the annular thrust portion is located at the center. In this case, the through hole is coaxial with the eccentric portion 11. The diameter of the through hole is larger than the diameter of the crankshaft 1 and smaller than the diameter of the eccentric portion 11.

[0054] Example 2

[0055] Based on the roller ring 31 in Example 1, this embodiment provides a compressor. The compressor includes at least one roller ring 31 described above. Furthermore, the compressor includes a pump assembly disposed within the compressor housing and a motor for providing mechanical energy. The pump assembly includes a crankshaft 1, a cylinder 6, an upper flange bearing, a lower flange bearing, and a thrust roller 3.

[0056] The thrust roller 3 is composed of two roller rings 31 axially symmetrically assembled on the eccentric portion 11 of the crankshaft 1, so that two roller rings 31 are set on the eccentric portion 11 of each crankshaft 1. The pump body assembly of the compressor also includes: a cylinder 6 providing a compression working chamber and a vane 5 therein; a crankshaft 1, which is inserted into the cylinder 6 and has an eccentric portion 11 on its shaft that cooperates with the vane 5. The eccentric portion 11 is located within the cylinder 6, wherein the two roller rings 31 are respectively mounted on the upper and lower portions of the eccentric portion to thrust the crankshaft 1 in the axial direction of the eccentric portion; a first flange bearing 2 mounted on the crankshaft 1 for axially limiting the roller ring 31 on the upper portion of the eccentric portion at the upper portion of the crankshaft 1; and a second flange bearing 4 mounted on the crankshaft 1 for axially limiting the roller ring 31 on the lower portion of the eccentric portion at the lower portion of the crankshaft 1. The pump body assembly uses two flange bearings to fix the cylinder 6 into a sealed working chamber.

[0057] The thrust roller 3 is assembled with the crankshaft 1 as follows: After the second flange bearing 4 (lower flange) is assembled with the cylinder 6, one roller ring (the lower ring) of the thrust roller 3 is placed on the end face of the lower flange. The eccentric portion of the crankshaft 1 is then placed within the lower roller ring to assemble the crankshaft 1. Finally, the other roller ring (the upper ring) of the thrust roller 3 is assembled with the eccentric portion of the crankshaft 1 to complete the assembly of the crankshaft 1 and the thrust roller 3. After the crankshaft 1 and the roller are assembled into an integral structure, the axial end face of the outer wall of the roller ring cooperates with the lower flange bearing to achieve axial constraint between the crankshaft 1 and the roller.

[0058] In this embodiment, corresponding assembly surfaces are provided on the roller rings and the crankshaft 1 and other components. Specifically, the roller ring 31 has a contact surface S4. The roller 3 is formed by the contact surfaces S4 of the two roller rings 31, which are in contact and matched, and the two roller rings 31 are assembled and combined axially symmetrically in the upper and lower directions. The roller ring 31 has an inner wall axial end face S1 and an inner wall radial circumferential surface S2. The crankshaft 1 has an eccentric portion end face S6 that matches the inner wall axial end face S1 of the roller 3 and an eccentric portion radial outer circumferential surface S5 that matches the inner wall radial circumferential surface S2 of the roller 3. The inner wall axial end face S1 of the roller ring 31 contacts and matches the eccentric portion end face S6 of the crankshaft 1, and the inner wall radial circumferential surface S2 of the roller ring 31 contacts and matches the eccentric portion radial outer circumferential surface S5 of the crankshaft 1, thereby realizing the assembly of the roller ring on the eccentric portion of the crankshaft 1, so that the roller ring 31 and the crankshaft 1 form an integral structure. It should be noted that the roller rings rely on the gravity of the upper roller to contact the lower roller, and the two rollers can rotate relative to each other, not in a relatively static state. The relative rotation between the two is also conducive to wear between the eccentric portion and the roller. The roller ring 31 also has an outer wall axial end face S3. The second flange bearing 4 has an axial upper end face S7 that cooperates with the outer wall axial end face S3 of the roller ring 31. The outer wall axial end face S3 of the roller ring 31 contacts and cooperates with the axial upper end face S7 of the lower flange 4. The deadweight of the crankshaft 1 and the roller 3 acts on the axial upper end face S7 of the lower flange 4, realizing axial constraint of the crankshaft 1 and the roller 3.

[0059] The assembly of the entire pump body is as follows: first, assemble the lower flange and cylinder 6 with screws, then place the roller on the end face of the lower flange, and then pass the short shaft of the crankshaft through the center of the roller to contact the inner circumference of the neck of the lower flange. Then, pass the upper roller through the long shaft of the crankshaft and buckle it on the eccentric part of the crankshaft. Then, pass the upper flange through the short shaft of the crankshaft, match the screw holes of the upper flange, lower flange and cylinder 6, and connect the three with screws to form a closed working chamber. The crankshaft and roller are axially constrained, but can rotate freely around the axis.

[0060] It should be noted that in this embodiment, the minimum diameter D1 of the roller ring 31's inner wall surface is greater than the crankshaft's major axis diameter D4, and the minimum diameter D1 of the roller ring's inner wall surface is greater than the crankshaft's minor axis diameter D5. The maximum diameter D2 of the radial circumferential surface S2 of the roller ring 31's inner wall is ≥ the crankshaft's eccentric diameter D4. The maximum axial height H1*2 of the radial circumferential surface S2 of the roller ring 31's inner wall is equal to the axial height H3 of the crankshaft's eccentric portion. The overall axial height H2*2 of the roller ring 31 is equal to the axial height H4 of the cylinder 6's working chamber. The inner wall surfaces S1 and S2 of the roller ring 31 are provided with grooves 311, which include a first groove 312 and / or a second groove 311.

[0061] When the compressor of this embodiment is working, the inner wall axial end surface S1 of the roller ring 31 contacts the end surface S6 of the eccentric portion of the crankshaft 1, and the inner wall radial circumferential surface S2 of the roller ring 31 contacts the radial outer circumferential surface S5 of the eccentric portion of the crankshaft 1. The roller ring 31 is axially symmetrically assembled on the upper and lower ends of the eccentric portion of the crankshaft 1, so that the two roller rings 31 are assembled on the eccentric portion of the crankshaft 1, so that the crankshaft 1 and the roller 3 become an integral structure. Under the action of the gravity of the crankshaft 1 and the roller 3, the bearing of the lower flange 4 is squeezed. The axial end face S3 of the outer wall of the roller ring 31 contacts the upper end face S7 of the bearing of the lower flange 4. The lower flange 3 generates an axial support force to constrain the axial displacement of the crankshaft 1 during rotation. At this time, the maximum outer diameter of the axial displacement support thrust surface of the crankshaft 1 and the roller 3 is the maximum outer diameter D3 of the roller ring 31. The stability of the crankshaft 1 during rotation is better, and during the rotation of the crankshaft, the upper and lower roller rings 31 can rotate relative to the crankshaft 1, and the relative sliding friction between the crankshaft 1 and the roller ring 31 is more uniform. In addition, a number of annular grooves 311 are provided on the inner wall surfaces S1 and S2 of the roller ring 3. As the crankshaft 1 rotates, the lubricating oil flows from the central oil hole of the crankshaft 1 through the transverse oil supply hole of the crankshaft 1 and into the contact surface between the roller ring 31 and the eccentric part of the crankshaft 1, thereby improving the lubrication effect and reducing the friction and wear of the contact surface. Moreover, due to the arrangement of the annular grooves 311 on the inner wall surfaces S1 and S2 of the roller 3, when the eccentric part of the crankshaft 1 is deformed, the annular grooves 311 can increase the elastic deformation of the eccentric part of the crankshaft 1 after deformation, thereby further reducing the friction and wear of the contact surface.

[0062] The rotor compressor structure proposed in this invention improves the crankshaft thrust structure of existing compressors by increasing the maximum outer diameter of the thrust surface and enhancing the stability of the crankshaft's axial restraint. Furthermore, during compressor operation, the rollers can fully rotate relative to the crankshaft, improving the uniformity of sliding friction between the vanes 5 or the crankshaft and the rollers, reducing excessive wear between components and increasing compressor efficiency. Furthermore, an annular groove between the rollers and the eccentric portion enhances lubrication between the crankshaft and rollers, while also increasing the elastic deformation of the crankshaft's eccentric portion after deformation, further reducing friction and wear caused by deformation and improving compressor reliability.

[0063] It should be noted that the compressor in Example 2 can be installed in, but is not limited to, equipment that requires a compressor, such as air conditioners.

[0064] While the exemplary embodiments of the present disclosure have been specifically illustrated and described above, it should be understood that the present disclosure is not limited to the detailed structures, configurations, or implementations described herein; rather, the present disclosure is intended to encompass various modifications and equivalent configurations within the spirit and scope of the appended claims.

Claims

1. A roller ring for a rotary compressor, wherein the rotary compressor has a crankshaft, and an eccentric portion is provided on the shaft of the crankshaft, characterized in that: The roller ring includes: an annular sleeve and an annular thrust portion, wherein the annular sleeve and the annular thrust portion are sleeved on the upper part or the lower part of the eccentric portion in cooperation with each other; The side wall of the annular sleeve forms a sleeve space for sleeve-mounting the eccentric portion; the annular thrust portion is provided at one end of the annular sleeve and is used to push against the top or bottom of the eccentric portion to limit the eccentric portion in its axial direction; the annular thrust portion is provided with a through hole, the through hole being used for the shaft of the crankshaft to pass through so that the annular thrust portion can push against the eccentric portion; The inner wall of the annular thrust portion that stops the eccentric portion from being pushed is provided with a second friction-reducing structure, and the second friction-reducing structure is used to reduce the friction between the annular thrust portion and the eccentric portion; The second friction reducing structure includes a second groove provided on the inner wall of the annular thrust portion that stops the eccentric portion from pushing, and the second groove is used for storing lubricating oil or accommodating balls.

2. The roller ring for a rotary compressor according to claim 1, characterized in that: The second groove is an annular groove formed on the inner wall of the annular thrust portion that stops the eccentric portion from being pushed.

3. The roller ring for a rotary compressor according to claim 1, characterized in that: The second grooves are a plurality of micro-hole grooves opened on the inner wall of the annular thrust portion that stops the eccentric portion from thrusting.

4. The roller ring for a rotary compressor according to any one of claims 1 to 3, characterized in that: The inner wall of the annular sleeve is provided with a first friction reducing structure, and the first friction reducing structure is used to reduce the friction between the annular sleeve and the eccentric part.

5. The roller ring for a rotary compressor according to claim 4, characterized in that: The first friction reducing structure includes: a first groove arranged on the inner wall of the annular sleeve, and the first groove is used for storing lubricating oil or accommodating balls.

6. The roller ring for a rotary compressor according to claim 5, characterized in that: The first groove is a circumferential sliding groove opened on the inner wall of the annular sleeve in the circumferential direction of the annular sleeve.

7. The roller ring for a rotary compressor according to claim 5, characterized in that: The first grooves are a plurality of microporous grooves evenly distributed on the inner wall of the annular sleeve.

8. The roller ring for a rotary compressor according to claim 1, characterized in that: The roller ring is coaxially arranged with the eccentric portion, and the through hole is located at the center of the annular thrust portion, wherein the aperture of the through hole is larger than the diameter of the crankshaft and smaller than the diameter of the eccentric portion.

9. A compressor, characterized in that: The compressor comprises: at least one roller ring according to any one of claims 1-8.

10. The compressor according to claim 9, characterized in that There are two roller rings, and the compressor further includes: Cylinder and the slide inside it; A crankshaft, the crankshaft being passed through the cylinder, and the crankshaft shaft being provided with an eccentric portion cooperating with the slide, the eccentric portion being located in the cylinder; wherein the two roller rings are respectively sleeved on the upper and lower portions of the eccentric portion to prevent the crankshaft from thrusting in the axial direction of the eccentric portion; a first flange bearing, sleeved on the crankshaft, for limiting the position of the roller ring on the upper part of the eccentric part in the axial direction on the upper part of the crankshaft; The second flange bearing is sleeved on the crankshaft and is used to limit the roller ring at the lower part of the eccentric part in the axial direction at the lower part of the crankshaft.

11. An air conditioner, characterized in that: The air conditioner includes the compressor according to claim 9 or 10.

Images