CN210565070U

CN210565070U - Compression mechanism of scroll compressor and scroll compressor

Info

Publication number: CN210565070U
Application number: CN201920902551.5U
Authority: CN
Inventors: 许华; 赵景莲; 张跃
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2019-06-14
Filing date: 2019-06-14
Publication date: 2020-05-19
Anticipated expiration: 2029-06-14

Abstract

The utility model relates to a scroll compressor's compressing mechanism and scroll compressor. In one aspect, a compression mechanism comprises: a non-orbiting scroll member and an orbiting scroll member engaged with each other to define an operating fluid chamber including a suction chamber, the orbiting scroll member having an end plate, the non-orbiting scroll member having a key groove; an anti-rotation device coupled with the non-orbiting scroll part and the orbiting scroll part, respectively, such that the orbiting scroll part can orbit with respect to the non-orbiting scroll part, the anti-rotation device having a key coupled to the key groove; and a lubrication passage provided in the end plate, wherein an oil outlet hole of the lubrication passage is positioned such that: the oil outlet hole is alternately in fluid communication with the key groove and the suction chamber during one orbiting revolution of the orbiting scroll part, or the oil outlet hole is always in fluid communication with the key groove and the suction chamber during a part of the angle during one orbiting revolution of the orbiting scroll part. According to the utility model discloses, can lubricate rotation preventing device and vortex effectively.

Description

Compression mechanism of scroll compressor and scroll compressor

Technical Field

The utility model relates to a compressor field, especially, this compression mechanism has and is used for carrying out lubricated passageway lubricated to compression mechanism's cross sliding ring and scroll compression mechanism.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

A scroll compressor is a positive displacement compressor having a compression mechanism composed of a movable scroll member and a fixed scroll member. When the movable scroll part moves relative to the fixed scroll part, in order to prevent the movable scroll part from rotating in the moving process, an anti-rotation device, such as a cross slip ring, capable of effectively preventing the movable scroll part from rotating is arranged. The motor drives a compression mechanism (e.g., an orbiting scroll member) via a rotating shaft to compress a working fluid (e.g., a refrigerant). Scroll compressors require sufficient lubricant (e.g., oil) to effect lubrication of the orbiting and non-orbiting scroll members and lubrication of the oldham ring during operation.

Fig. 1, 2a and 2b show a prior art scroll compressor and its lubrication passages. In the compressor 100 shown in fig. 1, the compression mechanism 110 is constituted by a fixed scroll member 150 and an orbiting scroll member 160. More specifically, non-orbiting scroll member 150 includes an end plate 154, a spiral vane 156 formed at one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. Orbiting scroll member 160 includes an end plate 164, a hub 162 formed on one side of the end plate, and a spiral vane 166 formed on the other side of the end plate. Spiral vanes 156 and 166 of non-orbiting and orbiting

scroll members

150 and 160 mesh with each other to form a series of working fluid chambers therebetween that gradually decrease in volume moving from a radially outer side to a radially inner side. The radially outermost working fluid chamber is at suction pressure and is therefore referred to as a suction chamber, and the radially innermost working fluid chamber is at discharge pressure and is therefore referred to as a discharge chamber. The intermediate working fluid chamber is between the suction pressure and the discharge pressure and is therefore also referred to as the medium pressure chamber.

Fig. 2a and 2b are longitudinal sectional views of the compression mechanism 110 of the compressor 100. As shown in fig. 2a and 2b, an oldham ring 178 is installed in the recess 169 (also referred to as a key groove 169) of the non-orbiting scroll member and the recess of the orbiting scroll member to prevent the orbiting scroll member 160 from rotating. Fig. 2a shows a key of the oldham ring 178 which is in contact with the orbiting scroll part 160 (hereinafter referred to as an orbiting scroll key) and a structure for lubricating the key. As shown in the drawing, the lubricant oil pumped from the bottom oil sump is stored in the concave pocket of main bearing housing 140, and the lubricant oil is pushed out of main bearing housing 140 by the relative movement of orbiting scroll member 160 and the concave pocket of main bearing housing 140, and is further supplied to the orbiting scroll key of oldham ring 178 through the oil supply route a → B → C, so as to lubricate the orbiting scroll key of oldham ring 178. In fig. 2b, a key (hereinafter referred to as a non-orbiting scroll key) where the oldham ring 178 contacts the non-orbiting scroll part 150 and a structure for lubricating the key are shown. Similar to the foregoing, the lubricating oil is pushed out of main bearing housing 140 by the relative movement of orbiting scroll member 160 and the pockets of main bearing housing 140. However, differently, since the position of the non-orbiting scroll key of the oldham 178 is relatively high, the lubricating oil needs to be supplied to the non-orbiting scroll key of the oldham 178 through the oil supply route a → B → C → D to lubricate the non-orbiting scroll key of the oldham 178. One disadvantage of such lubrication channels is that: compared with the oil supply route of the movable scroll key of the oldham ring 178, the process from C → D is increased due to the higher position of the fixed scroll key of the oldham ring, which results in the lubricating oil needing to do extra work for overcoming the gravity, so the lubricating oil is difficult to reach the position where the fixed scroll key of the oldham ring is contacted with the key slot, and the lubricating condition of the fixed scroll key of the oldham ring is relatively poor compared with the movable scroll key of the oldham ring. In summary, in the prior art lubrication passages, there is no oil outlet hole for the non-orbiting scroll key groove at a high position, or the related oil outlet hole is always open to the related key groove, or a single oil outlet hole for alternately supplying oil to the oldham ring and the scroll suction chamber during one revolution of the scroll is not provided.

Accordingly, there is a need for an improved compression mechanism of a scroll compressor and a lubrication passage thereof that can more effectively and moderately lubricate the orbiting and non-orbiting scroll members and the oldham ring.

SUMMERY OF THE UTILITY MODEL

The general outline of the present invention is provided in this section, not a full scope of the present invention or a full disclosure of all the features of the present invention.

The object of the present invention is to solve one or more of the above mentioned technical problems. For example, the technical scheme of the utility model can lubricate moving vortex part and fixed vortex part and oldham ring effectively, moderately, compromise the equilibrium.

In order to solve one or more of the above-mentioned technical problems, according to an aspect of the present invention, there is provided a compression mechanism of a scroll compressor, the compression mechanism including: the scroll compressor comprises a fixed scroll component and an orbiting scroll component, wherein the fixed scroll component and the orbiting scroll component are meshed with each other to limit an operating fluid cavity, the operating fluid cavity comprises a suction cavity, the orbiting scroll component is provided with an end plate, and the fixed scroll component is provided with a key groove; the anti-rotation device is respectively connected with the fixed scroll part and the movable scroll part, so that the movable scroll part can orbit relative to the fixed scroll part in a translation manner, and the anti-rotation device is provided with a key connected to the key groove; and at least one lubrication channel disposed in the end plate. The oil outlet hole of the lubrication passage is positioned such that: the oil outlet hole is alternately in fluid communication with the key groove and the suction chamber during one orbiting revolution of the orbiting scroll part, or the oil outlet hole is always in fluid communication with the key groove and the suction chamber during a part of the angle during one orbiting revolution of the orbiting scroll part.

In the above compression mechanism, the lubrication passage further includes an oil inlet hole and a cross hole communicating the oil inlet hole with the oil outlet hole.

In the above-described compression mechanism, the scroll compressor includes a main bearing housing for supporting the compression mechanism, an oil storage cavity is formed in the main bearing housing, and the oil inlet hole is communicated with the oil storage cavity, or the movable scroll part further has a boss portion adapted to be driven by a drive shaft of the scroll compressor, an oil storage region is formed in the boss portion, and the oil inlet hole is communicated with the oil storage region.

In the compression mechanism, for the scheme that the oil outlet hole is always in fluid communication with the key groove, the oil outlet hole is opened at the side part of the end plate and is communicated with the key groove.

In the above compression mechanism, the fixed scroll member includes an outer peripheral wall, and an angular range in which the oil outlet hole is located radially inside the outer peripheral wall and is simultaneously in fluid communication with the key groove and the suction chamber in one orbiting revolution of the movable scroll member is defined as an inside angle_，The inside angle satisfies the following relationship: the inner angle is more than 0 and less than or equal to 180 degrees, wherein when the oil outlet is in the inner angle range, the centrifugal force generated by the movable vortex component in the orbiting process does negative work to inhibit the lubricating oil from being conveyed to the oil outlet in the lubricating channel.

In the above compression mechanism, in the case where the oil outlet hole is alternately in fluid communication with the key groove and the suction chamber, the oil outlet hole is opened to the surface of the end plate facing the non-orbiting scroll member.

In the compression mechanism, the oil inlet hole of the lubricating channel is positioned on the radial inner side of the compression mechanism, the oil outlet hole is positioned on the radial outer side of the compression mechanism, and the lubricating channel enables the lubricating oil to be conveyed from the oil inlet hole to the oil outlet hole in the lubricating channel through the pressure difference between the inlet of the oil inlet hole and the outlet of the oil outlet hole and/or the centrifugal force generated by the movable scroll part in the orbiting process.

In the above compression mechanism, the fixed scroll member includes an outer peripheral wall, and an angle at which the oil outlet hole is located radially outside the outer peripheral wall to fluidly communicate with the key groove in one orbiting revolution of the orbiting scroll member is defined as a first angle θ₁First angle theta₁The following relationship is satisfied: theta is more than 0₁Less than or equal to 180 degrees, wherein, when the oil outlet hole is at the first angle theta₁In the range of (a), the centrifugal force does positive work to help transport the lubricating oil from the oil inlet hole to the oil outlet hole in the lubrication passage.

In the above-mentioned compressorIn the structure, an angular range in which the oil outlet hole is located radially inside the outer peripheral wall to fluidly communicate with the suction chamber in one revolution of the orbiting scroll member is defined as a second angle θ_2，Second angle theta₂The following relationship is satisfied: theta is more than 0₂Less than or equal to 180 degrees, wherein, when the oil outlet hole is at the second angle theta₂When the oil pressure is within the range of (2), the centrifugal force does negative work to inhibit the lubricating oil from being conveyed from the oil inlet hole to the oil outlet hole in the lubricating channel.

In the above compression mechanism, the fixed scroll member includes an outer peripheral wall, and an angle at which the oil outlet hole is located radially outside the outer peripheral wall to fluidly communicate with the key groove in one orbiting revolution of the orbiting scroll member is defined as a first angle θ₁An angular range in which the oil outlet hole is located radially inside the outer peripheral wall so as to be in fluid communication with the suction chamber is defined as a second angle theta_2，Wherein the first angle theta₁And a second angle theta₂The following relationship is satisfied: theta₁＞θ₂Such that the lubrication passage is in fluid communication with the keyway over a greater angular range than the suction cavity for one revolution of the orbiting scroll member.

In the above compression mechanism, the fixed scroll part has two key grooves, and two lubrication passages are provided in the end plate in one-to-one correspondence with the two key grooves.

In order to solve one or more of the above-mentioned technical problems, according to another aspect of the present invention, a scroll compressor is provided. The scroll compressor comprises the compression mechanism.

The compression mechanism of the scroll compressor and the lubricating structure thereof according to the present invention have advantages as follows, for example. The utility model discloses an among scroll compressor's the lubricating structure, can realize that the position more leans on the oil outlet that is close to more decide the vortex keyway to can lubricate the deciding vortex key of easy wearing and tearing effectively. The utility model discloses an among the scroll compressor's lubricating structure, can make the oil outlet intermittently with decide vortex keyway fluid intercommunication, consequently can avoid excessively to deciding the vortex keyway fuel feeding. The utility model discloses an among scroll compressor's lubricating structure, the in-process that moves the vortex part and orbit the round lubricates cross sliding ring and vortex alternately via same oil outlet, perhaps, lubricates the cross sliding ring all the time and lubricates the vortex intermittently via same oil outlet, consequently can compromise lubricated cross sliding ring and vortex balanced. The utility model discloses an in the lubricating structure of scroll compressor of embodiment, when oil outlet and decide vortex keyway fluid intercommunication, centrifugal force helps the fuel feeding, and when oil outlet and the chamber fluid intercommunication of breathing in, centrifugal force restraines the fuel feeding (promptly, reduces the sensitivity of vortex distributive value to speed), thereby can avoid too much oil to get into the vortex part effectively and can control the oil circulation rate effectively when ensureing appropriate vortex lubrication.

Drawings

The technical features of one or more embodiments of the present scroll compressor and lubrication passages of the scroll compressor and the lubrication passages of the scroll compressor of the present invention are illustrated in the accompanying drawings, in which:

FIG. 1 is a longitudinal sectional view of a conventional scroll compressor;

FIG. 2a is a longitudinal cross-sectional view of a compression mechanism of a conventional scroll compressor showing a key of an Oldham ring contacting an orbiting scroll member;

FIG. 2b is a longitudinal cross-sectional view of the compression mechanism of the prior art scroll compressor showing the keys of the Oldham ring that contact the non-orbiting scroll member;

fig. 3 is a longitudinal sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention;

fig. 4 is a cross-sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention;

fig. 5a is a partial cross-sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention, wherein an oil outlet is in fluid communication with a suction chamber;

fig. 5b is a partial cross-sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention, wherein the oil outlet is in fluid communication with the key groove;

FIG. 6 is a view illustrating an embodiment according to the present inventionA schematic diagram of the change in the position of the oil outlet hole during the movement of the compression mechanism of the scroll compressor of the embodiment, in which the oil outlet hole is shown at the first angle θ₁Is in fluid communication with the keyway and at a second angle theta₂Is in fluid communication with the suction lumen;

fig. 7 is a longitudinal sectional view of a compression mechanism of a scroll compressor according to a second embodiment of the present invention; and

fig. 8a and 8b are longitudinal sectional views of a compression mechanism of a scroll compressor according to a third embodiment of the present invention.

Detailed Description

The invention is described in detail below with the aid of specific embodiments with reference to the attached drawings. The following detailed description of the invention is merely for purposes of illustration and is in no way intended to limit the invention, its application, or uses.

The utility model provides a scroll compressor's lubrication passage, this lubrication passage are used for lubricating scroll compressor's compressing mechanism. More specifically, the lubrication passage alternately lubricates the scroll and the oldham ring during operation of the scroll compressor.

First, the general configuration and operation principle of the lubrication passage of the scroll compressor according to the present invention will be described in brief with reference to fig. 3 to 6.

Fig. 3 is a longitudinal sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention, and fig. 4 is a transverse sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention. The compression mechanism 210 of the scroll compressor shown in fig. 3 and 4 is constituted by a fixed scroll member 250 and an orbiting scroll member 260. More specifically, the non-orbiting scroll member 250 includes an end plate 254, a spiral-shaped vane formed at one side of the end plate, and an exhaust port 252 formed at a substantially central position of the end plate. Orbiting scroll member 260 includes an end plate 264, a hub 262 formed on one side of the end plate, and a spiral vane 266 formed on the other side of the end plate. An oil reservoir region is formed in the hub portion of orbiting scroll member 260. The spiral vanes 266 of non-orbiting scroll member 250 and orbiting scroll member 260 mesh with each other to form therebetween a series of operating fluid chambers of decreasing volume from the radially outer side to the radially inner side, including a suction chamber. Anti-rotation means, such as corresponding keys of an oldham ring 278, are mounted within recess 269 of the non-orbiting scroll member (also referred to as keyway 269) and recess (not shown) of the orbiting scroll member to prevent rotation of the non-orbiting scroll member 260. At least one (two in the present embodiment) lubrication passage 245 is formed in an end plate 264 of the orbiting scroll member, and an oil outlet hole of the lubrication passage 245 is opened in a surface of the end plate 264 facing the non-orbiting scroll member 250. The lubrication passage 245 includes an oil inlet hole, a cross hole, and an oil outlet hole. The oil inlet of the lubrication passage 245 is in fluid communication with the oil reservoir in the hub portion of the orbiting scroll member 260, the cross bore of the lubrication passage 245 is blocked at both ends by plugs, and the oil outlet of the lubrication passage 245 is in alternate fluid communication with the key slot 269 of the non-orbiting scroll member and the suction chamber. When the oil outlet hole of the lubrication passage 245 is in fluid communication with the key groove 269, additionally compared to the lubrication passage of the related art, the oil-supplying driving force causes the lubricating oil to enter the key groove 269 through the lubrication passage 245 in a line of E → F → G → H, thereby lubricating the keys of the oldham ring 278 in the key groove 269. Specifically, the driving force for oil supply is composed of two parts: the pressure difference caused by the fact that the pressure of the oil inlet hole is higher than that of the oil outlet hole is always positive, namely, the lubricating oil can flow to the oil outlet hole from the oil inlet hole of the lubricating channel; and an inertial force (centrifugal force) caused by the movement of the movable scroll, the direction of the centrifugal force being constantly changed in accordance with the movement of the movable scroll, and sometimes performing positive work on the lubricating oil, i.e., helping the lubricating oil to flow from the oil inlet hole to the oil outlet hole of the lubricating passage, and sometimes performing negative work on the lubricating oil, i.e., hindering the lubricating oil from flowing from the oil inlet hole to the oil outlet hole of the lubricating passage. Specifically, when the oil outlet holes are in fluid communication with the key slot 269, the centrifugal force performs positive work to facilitate the transfer of lubricant from the oil inlet holes to the oil outlet holes in the lubrication passage, and when the oil outlet holes are in fluid communication with the suction chamber, the centrifugal force performs negative work to inhibit the transfer of lubricant from the oil inlet holes to the oil outlet holes in the lubrication passage. Under the condition that the oil outlet hole is communicated with the air suction cavity in a fluid mode, when the movable vortex component runs at a medium-low speed, the centrifugal force can be smaller than the pressure difference between the oil inlet hole and the oil outlet hole, and therefore lubricating oil can still enter the air suction cavity; when the movable scroll part is operated at a high speed, the centrifugal force may be larger than the pressure difference between the oil inlet hole and the oil outlet hole, that is, the lubricating oil is prevented from being delivered from the oil inlet hole to the oil outlet hole, which contributes to reducing the oil circulation rate when the movable scroll part is operated at a high speed. Furthermore, compared with the prior art, when the oldham ring is lubricated, the oil outlet of the lubrication passage 245 is higher, and the lubricating oil can more easily enter the matching surface of the key of the oldham ring 278 and the key groove 269, so that the key of the oldham ring 278 in the key groove 269 can be better lubricated.

Fig. 5a is a partial cross-sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention, wherein an oil outlet is in fluid communication with a suction chamber. Fig. 5b is a partial cross-sectional view of a compression mechanism of a scroll compressor according to an embodiment of the present invention, in which an oil outlet is in fluid communication with a key groove. During one revolution of the orbiting scroll member in a translational manner, for one lubrication passage, the oil outlet is in fluid communication with the key slot over a range of angles for lubricating the oldham ring in the key slot (as shown in fig. 5 b); and in another angular range with the suction chamber for lubricating the scroll (as shown in figure 5 a). With the compression structure of this embodiment, the non-orbiting scroll member has two key grooves, and two lubrication passages are provided in the end plate in one-to-one correspondence with the two key grooves. In one revolution of the orbiting scroll member, when the oil outlet hole of the left lubrication passage is located at a position in fluid communication with the left key groove, the oil outlet hole of the right lubrication passage is located at a position in fluid communication with the right suction chamber (as shown in fig. 3), and when the oil outlet hole of the left lubrication passage is located at a position in fluid communication with the left suction chamber, the oil outlet hole of the right lubrication passage is located at a position in fluid communication with the right key groove (not shown). When the oil outlet is in fluid communication with the keyway, as described above, the centrifugal force F is applied to the lubrication passage_IThe direction from the directional oil outlet of inlet port, help lubricating oil to flow to the oil outlet from the inlet port to make more lubricating oil get into the keyway in order to lubricate the cross sliding ring, reduced the wearing and tearing of cross sliding ring. When the oil outlet is communicated with the air suction cavityTime, centrifugal force F_IIs directed from the oil outlet hole to the oil inlet hole, the flow of the lubricating oil from the oil inlet hole to the oil outlet hole is inhibited, thereby reducing the sensitivity of the swirl injection quantity to the speed, i.e., reducing or even stopping the supply of the lubricating oil when the swirl speed increases. This is of great significance to inverter compressors because even if the inverter compressor is operated at high speed, excessive lubrication oil will not enter the scroll due to the reduced sensitivity of the scroll oil injection amount to speed. In addition, when the oil outlet is communicated with the fluid of the air suction cavity, the sealing of the vortex is also facilitated, thereby improving the leakage in the vortex compression process, improving the performance and reducing the exhaust temperature.

Fig. 6 is a schematic view illustrating a change in the position of the oil outlet hole during the movement of the compression mechanism of the scroll compressor according to an embodiment of the present invention, in which the oil outlet hole is shown at a first angle θ₁Is in fluid communication with the keyway and at a second angle theta₂Is in fluid communication with the suction lumen. In fig. 6, the dotted line is the orbit of the orbiting scroll part, any point on the orbiting scroll part satisfies the orbit, four circles are the positions where the oil outlet holes may be located, R_orIs the orbiting radius of the orbiting scroll member. Non-orbiting scroll member 250 includes an outer peripheral wall 256. As described above, in one revolution of the orbiting scroll member 260, the angle at which the oil outlet hole is located radially outside the outer peripheral wall 256 and fluidly communicates with the key groove 269 is defined as the first angle θ₁And an angular range in which the oil outlet hole is located radially inside the outer peripheral wall 256 to be in fluid communication with the suction chamber is defined as a second angle theta₂. First angle theta₁And a second angle theta₂The following relationship is satisfied: theta is more than 0₁≤180°，0＜θ₂Not more than 180 DEG and theta_1＜θ₂. When the oil outlet hole is at the first angle theta₁Is in fluid communication with the keyway 269 for lubricating the oldham ring 278 within the keyway 269, and when the oil outlet is at the second angle θ₂When in the range of (1), the oil outlet hole is in fluid communication with the suction chamber for lubricating the scroll. Therefore, it is possible to alternately lubricate the oldham ring and the scroll and ensure that the orbiting scroll part makes one revolutionThe lubricating oil can lubricate the cross slip ring more. In addition, when the oil outlet hole is at the first angle theta₁When the centrifugal force does positive work to help the lubricant oil to be delivered from the oil inlet hole to the oil outlet hole in the lubrication passage, and when the oil outlet hole is at the second angle theta₂When the oil pressure is within the range of (2), the centrifugal force does negative work to inhibit the lubricating oil from being conveyed from the oil inlet hole to the oil outlet hole in the lubricating channel, so that the sensitivity of the vortex oil injection quantity to the speed is reduced.

Fig. 7 is a longitudinal sectional view of a compression mechanism of a scroll compressor according to a second embodiment of the present invention. The compression mechanism of the scroll compressor according to the second embodiment of the present invention is substantially the same as the compression mechanism of the scroll compressor according to the first embodiment except that, in the scroll compressor according to the second embodiment, the scroll compressor includes a main bearing housing 240 for supporting the compression mechanism, an oil storage cavity 241 is formed in the main bearing housing 240, and an oil inlet is communicated with the oil storage cavity.

Fig. 8a and 8b are longitudinal sectional views of a compression mechanism of a scroll compressor according to a third embodiment of the present invention. The compression mechanism of the scroll compressor according to the third embodiment of the present invention is substantially the same as the compression mechanism of the scroll compressor according to the first and second embodiments of the present invention except for the following points: the oil outlet holes of the lubrication passage 245 open to the side of the end plate 264 and open to the key groove 269. In one example, the compression mechanism may further include an additional lubrication passage AP (see fig. 8b) that allows the keyway to intermittently communicate with the suction cavity. Additional lubrication passages AP may be defined by apertures or indentations provided at the radially outer side of end plate 264 of orbiting scroll member 260 (which may communicate with keyway 269 on the lower side). Non-orbiting scroll member 250 includes an outer peripheral wall 256. In one orbiting revolution of the orbiting scroll member 260, an angle when the oil outlet hole is located at the radial outer side of the outer peripheral wall 256 to be in fluid communication with only the key groove 269 (shown in fig. 8a) is defined as a third angle, and an angle range when the oil outlet hole is located at the radial inner side of the outer peripheral wall 256 to be in fluid communication with both the key groove 269 and the suction chamber (shown in fig. 8b) is defined as a fourth angle (corresponding to an inner angle according to the present invention). The fourth angle satisfies the following relationship: the fourth angle is more than 0 and less than or equal to 180 degrees.

Further, with the compression mechanism 210 of the scroll compressor according to the third embodiment, when the oil outlet hole is in the range of the third angle, the additional lubrication passage AP is closed (see fig. 8a) and when the oil outlet hole is in the range of the fourth angle, the additional lubrication passage AP is opened (see fig. 8 b). Thus, in this embodiment, during one revolution of the orbiting scroll member 260, when the oil outlet hole of the lubrication passage 245 is located at a position in fluid communication with only the key groove 269 and not with the suction chamber, the lubrication passage lubricates only the oldham ring 278 (as shown in fig. 8a), and when the oil outlet hole of the lubrication passage 245 is located at a position in fluid communication with both the key groove 269 and the suction chamber, the lubrication passage lubricates both the oldham ring 278 and the key groove 269 (as shown in fig. 8 b). Thus, the oil outlet of the lubrication passage 245 is in fluid communication with the key groove 269 at all times during one revolution of the orbiting scroll member 260 to lubricate the oldham ring 278, and is in fluid communication with the suction chamber via the key groove 269 when the oil outlet is within the range of the fourth angle to lubricate the oldham ring 278 and the scroll at the same time. Also, the compression structure of the third embodiment can ensure that both the oldham ring and the scroll are lubricated in one lap of the orbiting scroll part, and the lubricating oil can lubricate the oldham ring more. Specifically, the cross slip ring can be lubricated all the time in one circle of the orbiting scroll part, and the scroll can be lubricated intermittently.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the specific embodiments described and illustrated in detail herein, and that various changes may be made to the exemplary embodiments by those skilled in the art without departing from the scope defined by the appended claims.

Claims

1. A compression mechanism of a scroll compressor, the compression mechanism comprising:

a non-orbiting scroll member and an orbiting scroll member meshing with each other to define an operating fluid chamber including a suction chamber, the orbiting scroll member having an end plate, the non-orbiting scroll member having a key groove;

an anti-rotation device coupled to the non-orbiting scroll member and the orbiting scroll member, respectively, such that the orbiting scroll member orbits in a translational manner with respect to the non-orbiting scroll member, the anti-rotation device having a key coupled to the key groove; and

at least one lubrication channel disposed in the end plate,

the oil outlet of the lubricating channel is arranged in a position that: the oil outlet hole is alternately in fluid communication with the key groove and the suction chamber during one orbiting revolution of the orbiting scroll part, or the oil outlet hole is always in fluid communication with the key groove and the suction chamber during a part of an angle during one orbiting revolution of the orbiting scroll part.

2. The compression mechanism as claimed in claim 1, wherein the lubrication passage further includes an oil inlet hole and a cross hole communicating the oil inlet hole with the oil outlet hole.

3. The compression mechanism of claim 2, wherein:

the scroll compressor comprises a main bearing seat for supporting the compression mechanism, an oil storage cavity is formed in the main bearing seat, and the oil inlet is communicated with the oil storage cavity, or

The orbiting scroll member further has a hub portion adapted to be driven by a drive shaft of the scroll compressor, an oil storage region being formed in the hub portion, and the oil inlet hole being in communication with the oil storage region.

4. The compression mechanism of any one of claims 1-3, wherein for a version in which the oil outlet is always in fluid communication with the keyway, the oil outlet opens into a side of the end plate and opens into the keyway.

5. The compression mechanism according to claim 4, wherein the non-orbiting scroll member includes an outer peripheral wall, and an angular range in which the oil outlet hole is located radially inside of the outer peripheral wall while being in simultaneous fluid communication with the key groove and the suction chamber in one orbiting revolution of the orbiting scroll member is defined as an inside angular range_，The inside angle satisfies the following relationship: and the inner angle is more than 0 and less than or equal to 180 degrees, wherein when the oil outlet is in the range of the inner angle, the centrifugal force generated by the movable scroll part in the orbiting process does negative work to inhibit the lubricating oil from being conveyed to the oil outlet in the lubricating channel.

6. The compression mechanism of any one of claims 1-3, wherein for a scheme in which the oil outlet holes are alternately in fluid communication with the key slots and the suction chambers, the oil outlet holes open to a surface of the end plate facing the non-orbiting scroll member.

7. The compression mechanism of claim 6, wherein the oil inlet hole of the lubrication passage is located radially inside the compression mechanism, the oil outlet hole is located radially outside the compression mechanism, and the lubrication passage causes the lubricant to be delivered from the oil inlet hole to the oil outlet hole in the lubrication passage by a pressure difference between an inlet of the oil inlet hole and an outlet of the oil outlet hole and/or a centrifugal force generated by the orbiting scroll member during the orbiting motion.

8. The compression mechanism according to claim 7, wherein the non-orbiting scroll member includes an outer peripheral wall, and an angle at which the oil outlet hole is located radially outside of the outer peripheral wall to be in fluid communication with the key groove in one orbiting revolution of the orbiting scroll member is defined as a first angle θ₁The first angle theta₁The following relationship is satisfied: theta is more than 0₁180 degrees or less, wherein, when the oil outlet hole is positioned at the first angleDegree theta₁In the range of (a), the centrifugal force performs positive work to help transport the lubricating oil from the oil inlet hole to the oil outlet hole in the lubricating passage.

9. The compression mechanism according to claim 8, wherein an angular range in which the oil outlet hole is located radially inside the outer peripheral wall to be in fluid communication with the suction chamber in one orbiting revolution of the orbiting scroll member is defined as a second angle θ_2，The second angle theta₂The following relationship is satisfied: theta is more than 0₂180 degrees or less, wherein, when the oil outlet hole is at the second angle theta₂When the oil outlet hole is in the range of (2), the centrifugal force does negative work to inhibit the lubricating oil from being conveyed from the oil inlet hole to the oil outlet hole in the lubricating channel.

10. The compression mechanism according to claim 7, wherein the non-orbiting scroll member includes an outer peripheral wall, and an angle at which the oil outlet hole is located radially outside of the outer peripheral wall to be in fluid communication with the key groove in one orbiting revolution of the orbiting scroll member is defined as a first angle θ₁An angular range in which the oil outlet hole is located radially inside the outer peripheral wall so as to be in fluid communication with the suction chamber is defined as a second angle θ_2，Wherein the first angle θ₁And the second angle theta₂The following relationship is satisfied: theta₁＞θ₂Such that the lubrication passage is in fluid communication with the keyway over a greater angular range than the suction cavity for one revolution of the orbiting scroll member.

11. The compression mechanism according to any one of claims 1 to 3, wherein the non-orbiting scroll member has two key grooves, and two lubrication passages are provided in the end plate in one-to-one correspondence with the two key grooves.

12. A scroll compressor, characterized by comprising a compression mechanism according to any one of claims 1 to 11.