JP6630580B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor. In particular, the present invention relates to a technique for reducing wear of a wall of a keyway in which a key of an Oldham link provided in a scroll compressor slides.

  The scroll compressor is provided with an Oldham link that regulates rotation of the orbiting scroll. The Oldham link has a pair of first keys inserted into a pair of keyways of the orbiting scroll, and a pair of second keys inserted into a pair of keyways of the bearing. Is perpendicular to the direction in which the second key can slide in the radial direction along the keyway.

  In order to reduce the abrasion of the wall of the key groove in which the key of the Oldham link slides, a hard member having high wear resistance is arranged on the wall of the key groove (Patent Document 1), or a coating made of a solid lubricant is formed. Is done.

JP-A-8-189480

Lubricating oil pumped from an oil reservoir in the housing through an oil supply path in the rotary shaft is supplied to sliding portions such as the rotary shaft, the orbiting scroll, the thrust plate, the bearing, and the Oldham link of the scroll compressor. However, during low-speed operation, the supply amount of the lubricating oil decreases, so it is necessary to reduce the wear of the sliding portion to ensure reliability.
In particular, it is necessary to reduce the wear of the key of the Oldham link far from the joint between the eccentric pin of the rotating shaft where the lubricating oil is present and the orbiting scroll, and the key groove in which the key slides.
SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll compressor capable of reducing wear of a key of an Oldham link and a key groove in which the key slides.

The inventor of the present invention has examined the condition of the keyway wall being worn by the use of the scroll compressor, and found that the key of the Oldham link was displaced relative to the keyway, for example, the keyway of the keyway. The amount of wear gradually increases toward the outer peripheral end. This indicates that the key is in contact with the key groove wall in an inclined state on the open end (outer peripheral side end) side of the key groove, so that the key groove is easily worn.
Further, when the use of the scroll compressor is started, the surface roughness of the key groove wall and the key changes until the sliding surface between the key and the key groove wall is adapted.
Therefore, when a shape and surface roughness simulating a state worn by use and a state where the surface was adapted by use were given to the wall of the keyway in advance and use was started, it was confirmed that wear was reduced.

The scroll compressor of the present invention based on such knowledge is provided with a fixed scroll fixed to the housing, a orbiting scroll coupled to the rotating shaft eccentrically and revolving with respect to the fixed scroll, and fixed to the housing. And a bearing for supporting the orbiting scroll, and an Oldham link interposed between the orbiting scroll and the bearing for restricting rotation of the orbiting scroll.
The Oldham link includes a first key that slides in a radial direction of a rotating shaft with respect to a wall of a key groove provided in the orbiting scroll, and a radial key that slides in a radial direction with respect to a wall of another key groove provided in a bearing. And a second key that slides on the second key.
And, assuming a flat reference surface on the wall of the key groove, the present invention provides an offset portion that is gradually offset from the reference surface toward at least one of the outer peripheral end and the inner peripheral end of the key groove. was closed to a wall, a portion comprising at least offset portion of the inner peripheral portion of the keyway, or the whole of the inner peripheral portion, the main body is orbiting scroll or bearing a separate, first key or the second It is a liner that can make surface contact with the key, and the offset part is shaped so that the rate of increase of the offset amount with respect to the reference plane gradually increases toward the outside or inside in the radial direction. Features.

In the scroll compressor of the present invention, the surface roughness Ra of the sliding surface including the surface of the offset portion in the wall is preferably 0.2 μm or less prior to the start of using the Oldham link.
“Surface roughness Ra” according to the present invention is based on JIS B 0601-2001.

In the scroll compressor of the present invention, at least a part including the offset portion of the inner peripheral portion of the keyway, or the entire inner peripheral portion is a liner separate from the main body which is the orbiting scroll or the bearing .

In the scroll compressor according to the aspect of the invention, the liner may be positioned in the sliding direction in which the first key or the second key slides by being unevenly fitted to the main body located on the back side. preferable.
“Concavo-convex fitting” refers to a configuration in which a concave portion and a convex portion are fitted.

  In the scroll compressor of the present invention, the liner is preferably formed in a substantially U-shape.

  In the scroll compressor according to the aspect of the invention, it is preferable that a liner groove for receiving an edge of the liner is formed at a bottom of the key groove.

In the scroll compressor according to the aspect of the invention, it is preferable that the liner has a bottom surface of the key groove and has a liner bottom portion that is press-fitted into the main body, and a liner wall portion that rises from the liner bottom portion and includes an offset portion.
Furthermore, in the scroll compressor of the present invention, it is preferable that a coating using a solid lubricant is formed on the surface of the liner.

A scroll compressor according to the present invention includes a fixed scroll fixed to a housing, an orbiting scroll coupled to the rotary shaft eccentrically and revolving orbiting relative to the fixed scroll, and a orbiting scroll fixed to the housing. A bearing to be supported, and an Oldham link interposed between the orbiting scroll and the bearing to regulate the rotation of the orbiting scroll, and the Oldham link is provided between the rotating shaft and a wall of a keyway provided in the orbiting scroll. A first key that slides in the radial direction, and a second key that slides in the radial direction of the rotating shaft with respect to the wall of another key groove provided in the bearing; Prior to the start of use of the link, a surface roughness Ra of 0.2 μm or less is set.
In the above configuration, it is preferable that at least a portion of the inner peripheral portion of the key groove in which the surface roughness Ra is set or the entire inner peripheral portion is a liner separate from the main body that is the orbiting scroll or the bearing.

  In the scroll compressor according to the aspect of the invention, the main body is formed with a liner accommodating portion that accommodates the liner and allows displacement of the liner in a sliding direction in which the first key or the second key slides. Is preferred.

  In the scroll compressor according to the aspect of the invention, it is preferable that the liner is swingably supported by a main body located on the back side.

  In the scroll compressor of the present invention, at least the liner of the liner and the inner peripheral portion of the keyway communicates with an oil sump present around the joint between the rotary shaft and the orbiting scroll, and the oil sump extends from the oil sump. It is preferable that an oil path for supplying lubricating oil to the wall of the groove is formed.

  In the scroll compressor of the present invention, it is preferable that a coating having lubricity is applied to the wall of the keyway.

  According to the present invention, an offset portion is provided on the wall of the key groove in which the key of the Oldham link slides, or the surface roughness Ra of the wall of the key groove is 0.2 μm or less. As will be described later, the wear of the key and the keyway can be reduced without causing the large wear peculiar to the initial stage of use.

It is a longitudinal section showing a scroll compressor. It is the elements on larger scale of FIG. 1, and shows the key of Oldham link. It is a whole perspective view of an Oldham link. (A) is a figure which shows the keyway of an orbiting scroll and the key of an Oldham link, (b) is a figure which shows the keyway of a bearing and the key of an Oldham link. 4A and 4B show a keyway according to the first embodiment, wherein FIG. 4A is a perspective view and FIG. 4B is a plan view. It is a perspective view showing other keyways concerning a 1st embodiment. It is a figure for explaining the state of abrasion of the keyway confirmed in defining the shape of the wall of the keyway where the first key slides. (A) is a schematic diagram showing a key inclined at the open end side of the key groove, (b) is a perspective view of the key groove, and (c) is a key in the direction of the arrow in (b). It is a figure which shows the image of the shape profile of the wall of a groove | channel. It is a figure showing the relation between surface roughness of the wall of a keyway, and wear depth. (A) is a figure which shows the example which formed the offset part in both the outer peripheral end side and the inner peripheral end side. (B) is a schematic diagram showing an oil film between a key and a key groove wall. (A)-(c) is a perspective view which shows the keyway concerning 2nd Embodiment. It is a perspective view showing a keyway concerning a 3rd embodiment. (A) And (b) is a perspective view which shows the keyway concerning the combination of 2nd Embodiment and 3rd Embodiment. It is a perspective view showing the keyway concerning the combination of a 2nd embodiment and a 3rd embodiment. (A) and (b) are perspective views showing a keyway according to a fourth embodiment. It is a perspective view showing a keyway concerning a 5th embodiment. It is a perspective view showing a keyway concerning a 6th embodiment. (A) And (b) is a perspective view which shows the keyway concerning 7th Embodiment. It is a top view showing the keyway concerning a 7th embodiment. (A)-(c) is a figure which does not show the component of the keyway concerning 8th Embodiment, (d) is a figure which shows the modification of a component.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
First, a configuration common to each embodiment described below will be described with reference to FIGS.
The scroll compressor 1 shown in FIGS. 1 and 2 includes a fixed scroll 2 and an orbiting scroll 3, an Oldham link 10 for restricting rotation of the orbiting scroll 3, a motor 4, a rotating shaft 5, bearings 6 and 7, And a housing 8.
The scroll compressor 1 constitutes a refrigerator or an air conditioner.
A suction pipe 91 and a discharge pipe 92 provided in the housing 8 are connected to a refrigerant circuit of a refrigerator or an air conditioner.

When a drive current is supplied to the stator 4A of the motor 4 by a drive circuit unit (not shown), the rotor 4B of the motor 4 rotates and a rotational driving force is output to the rotating shaft 5. The rotating shaft 5 is rotatably supported by bearings 6 and 7 fixed to the housing 8.
When the rotating shaft 5 is rotated, the orbiting scroll 3 coupled via a bearing 5B to an eccentric pin 5A provided at the upper end of the rotating shaft 5 revolves orbits with respect to the fixed scroll 2 fixed to the housing 8. Is done. At this time, the rotation of the orbiting scroll 3 is restricted by the Oldham link 10 (FIG. 3) interposed between the orbiting scroll 3 and the bearing 6.
By the turning of the orbiting scroll 3, the refrigerant in the housing 8 is sucked between the orbiting scroll 3 and the fixed scroll 2. Then, as the orbiting scroll 3 turns, the volume of the compression chamber R between the orbiting scroll 3 and the fixed scroll 2 decreases, so that the refrigerant is compressed in the compression chamber R. The bearing 6 supporting the end plate 3A of the orbiting scroll 3 bears the thrust load due to the pressure of the compressed refrigerant. The compressed refrigerant is discharged to the refrigerant circuit through the discharge pipe 92 via the discharge port 2P of the fixed scroll 2.

  Lubricating oil is stored at the bottom of the housing 8. The lubricating oil is pumped up by a pump 101 provided at the lower end of the rotating shaft 5 through an oil supply path 5C (FIG. 2) inside the rotating shaft 5, and the bearings 6, 7, the rotating shaft 5, the eccentric pin 5A, The scroll 3, the Oldham link 10, and a sliding portion such as a thrust plate (not shown) arranged between the bearing 6 and the orbiting scroll 3 are supplied.

The Oldham link 10 (also called Oldham coupling) will be described with reference to FIGS.
As shown in FIG. 3, the Oldham link 10 includes a pair of first keys 11, 11, a pair of second keys 12, 12, and an annular connecting portion 13 connecting these keys 11, 11, 12, 12. And
The first keys 11, 11, the second keys 12, 12, and the connecting portion 13 are integrally formed from a metal material such as an aluminum alloy.
The bearing 6 and the orbiting scroll 3 that slide with the Oldham link 10 are formed of a metal material such as an aluminum alloy.

The first keys 11 protrude out of the one surface 131 of the connecting portion 13, and the second keys 12 protrude out of the other surface 132 of the connecting portion 13.
The D1 direction connecting the first keys 11 and the D2 direction connecting the second keys 12 and 12 are both along the radial direction of the connecting portion 13 and are orthogonal to each other.
The first keys 11, 11 are formed in a rectangular parallelepiped shape extending along the direction D1.
The second keys 12, 12 are formed in a rectangular parallelepiped shape extending along the direction D2.

As shown in FIGS. 2 and 4A, the first key 11 is fitted into a key groove 20 formed in the end plate 3A of the orbiting scroll 3. A pair of key grooves 20 corresponding to the pair of first keys 11 (FIG. 3) are formed in the end plate 3A.
The first key 11 slides radially with a predetermined stroke with respect to the key groove 20. Hereinafter, unless otherwise specified, the “radial direction” is a radial direction passing through the axis of the rotating shaft 5 and the bearing 6.

As shown in FIGS. 2 and 4B, the second key 12 is fitted into a key groove 30 formed on a thrust surface 6 </ b> A of the bearing 6 facing the orbiting scroll 3. The bearing 6 has a pair of key grooves 30 corresponding to the pair of second keys 12 (FIG. 3).
The second key 12 slides in the radial direction at a predetermined stroke with respect to the key groove 30.
The direction in which the first key 11 can slide along the key groove 20 (D1 direction in FIG. 3) and the direction in which the second key 12 can slide along the key groove 30 (D2 direction in FIG. 3) are as follows. Are orthogonal.

  When the rotational force of the rotating shaft 5 (FIG. 2) is transmitted to the orbiting scroll 3 via the eccentric pin 5A, the first key 11 slides along the keyway 20 in the D1 direction, and the second key 12 The Oldham link 10 slides in the D2 direction along the key groove 30 in the D2 direction. Thereby, the orbiting scroll 3 revolves around the fixed scroll 2 while drawing a predetermined trajectory without rotating.

FIGS. 5A and 5B show the keyway 20 formed in the end plate 3A of the orbiting scroll 3 from the back side (lower side) of the end plate 3A.
The key groove 20 is recessed at a predetermined depth from the back surface of the end plate 3A of the orbiting scroll 3.
The keyway 20 extends radially toward the scroll center by a predetermined distance from the outer peripheral edge 3B of the orbiting scroll 3. An outer peripheral end 20 </ b> A of the key groove 20 is open to the outside of the orbiting scroll 3. The inner peripheral end 20B of the key groove 20 is formed in an arc shape in plan view.

An inner peripheral portion 201 of the keyway 20 rises vertically from a flat bottom 202 of the keyway 20.
The first key 11 (shown by a two-dot chain line in FIG. 5B) reciprocates along the wall 21 of the key groove 20 in the radial direction while the orbiting scroll 3 makes one rotation while being guided by the key groove 20. I do. As shown in FIG. 4A, the first key 11 reciprocates within a range Rg1 from the outer peripheral end 20A of the key groove 20 to the vicinity of the inner peripheral end 20B.
The first key 11 slides on one surface 21 of the two surfaces 21 and 22 (FIG. 5B) of the key groove 20 which is determined by the rotation direction of the orbiting scroll 3. The surface on which the first key 11 slides is referred to as a wall 21 of the key groove 20.
The wall 21 of the keyway 20 is preferably formed by a liner 23 separate from the end plate 3A of the orbiting scroll 3, as shown in FIG.

Since the orbiting scroll 3 that is the base material of the key groove 20 and the liner 23 are separate bodies, a material different from the base material of the key groove 20, preferably, a material that is hard and hard to wear can be used for the liner 23. The liner 23 is preferably harder than the base material of the key groove 20 at least at a predetermined thickness from the surface (sliding surface). By appropriate surface processing and surface treatment, the hardness of the surface of the liner 23 can be increased.
In addition, since the sliding surface (wall 21) is formed by the liner 23 which is separate from the base material of the key groove 20, it is easier than a case where a later-described crowning or polishing is performed on the base material of the key groove. Can be applied to the liner 23.
The same applies to the liner 28 (FIG. 6) arranged in the keyway 30.

FIG. 6 shows a keyway 30 formed in the bearing 6. The surface on which the second key 12 (FIGS. 3 and 2) slides is referred to as a wall 31 of the key groove 30.
The keyway 30 is recessed from the thrust surface 6A of the bearing 6. The outer peripheral end 30A and the inner peripheral end 30B of the key groove 30 are formed in an arc shape in plan view.
The second key 12 (FIGS. 3 and 2) reciprocates along the wall 31 of the key groove 30 in the radial direction while the orbiting scroll 3 makes one rotation while being guided by the key groove 30. The second key 12 reciprocates within a range Rg2 (FIG. 4B) between the inner peripheral end 30B and the outer peripheral end 30A of the key groove 30.

The ranges Rg1 and Rg2 (FIG. 4) in which the first key 11 and the second key 12 slide with respect to the key grooves 20 and 30 are merely examples, and are along the walls 21 and 31 of the key grooves 20 and 30. The sliding range is appropriately determined.
In relation to the strokes of the first key 11 and the second key 12, the sliding ranges Rg1, Rg2 of the key grooves 20, 30 and whether or not the outer peripheral end of the key grooves are opened are determined.

[First Embodiment]
Hereinafter, specific configurations of the first key 11 and the second key 12, the key groove 20, and the key groove 30 will be described.
The first embodiment has main features in the shape of the wall 21 of the key groove 20 (an offset portion 21A described later) and the surface roughness Ra of the key groove 30. All of these features are aimed at reducing the wear of the keys 11 and 12 and the key grooves 20 and 30.

As described above, although the lubricating oil is supplied to the upper end of the rotary shaft 5 from the reservoir in the housing 8, the lubricating oil is supplied from the end plate 3 </ b> A of the orbiting scroll 3, the thrust plate (not shown), and the bearing 6. It is difficult to sufficiently supply the lubricating oil to the Oldham link 10 through a gap such as the thrust surface 6A.
In particular, during low-speed operation, the speed of the lubricating oil along the sliding surface is low, and the pressure of the lubricating oil due to the wedge action of the lubricating oil is low. Therefore, it is difficult to sufficiently form an oil film.
Moreover, regarding the key groove 20, it is difficult to hold the lubricating oil at the open outer peripheral end 20A.
As described above, it is important to reduce wear even when the keys 11 and 12 of the Oldham link 10 contact the walls 21 and 31 of the key grooves 20 and 30, respectively.

First, in determining the shape of the wall 21 of the key groove 20, a description will be given of a confirmed state of wear of the key groove 40 (FIG. 7).
FIG. 7C shows a result of performing a durability test corresponding to use (operation) for a predetermined period of time on a scroll compressor that has not been used except for a test run for operation confirmation, and as a result, an initial state (durability test) was obtained. The surface shape of the wall 41 of the keyway 40 worn from the front) is schematically shown.
The horizontal axis in FIG. 7 (c) corresponds to the sliding direction indicated by the arrow in FIG. 7 (b). As shown in FIG. 7C, the wear depth (amount of wear) of the wall 41 increases from the inner peripheral end 40B of the keyway 40 toward the open outer peripheral end 40A. The broken line shown in FIG. 7C corresponds to the flat surface of the wall 41 in the initial state.
The reason why the wear amount of the wall 41 increases toward the open end (outer end 40A) of the key groove 40 is mainly at the open end side (40A side) of the key groove 40 as shown in FIG. This is because the first key 11 is reciprocally displaced while being inclined with respect to the wall 41.
At the open end (edge) of the key groove 40 where the inclination angle of the first key 11 is maximum, the amount of wear becomes maximum.

Based on the profiling data of the surface shape of the wall 41 shown in FIG. 7C, in this embodiment, as shown in FIG. 5B, a part of the wall 21 is gradually offset with respect to the reference plane 210. Let me. The reference surface 210 is a flat surface assumed on the surface of the wall 21 and corresponds to the flat surface of the wall 41 in the initial state shown by the broken line in FIG.
The wall 21 has an offset portion 21A that is offset with respect to the reference plane 210 toward the outer peripheral end 20A. The maximum offset amount Of of the offset portion 21A with respect to the reference plane 210 is, for example, about 15 to 20 μm. The offset portion 21A is illustrated with an exaggerated offset amount. In FIG. 5A, the illustration of the offset portion 21A is omitted.
There is no shaded portion in FIG. The surface of the offset portion 21A is indicated by 21S.
The shape of the surface 21S of the offset portion 21A simulates the surface shape of the wall 21 worn by use (FIG. 7C). The offset portion 21 </ b> A is gradually and smoothly retracted with respect to the reference plane 210 with respect to the reference plane 210.

As shown in FIG. 5B, the wall 21 including the offset portion 21A is formed by a liner 23 provided on the end plate 3A. The liner 23 has a rectangular plate shape, and is arranged in a concave portion 3C formed in the end plate 3A so as to be depressed from the inner peripheral portion 201 of the key groove 20. The surface of the liner 23 and the surface of the inner peripheral portion 201 are flush with each other. The thickness of the liner 23 can be appropriately set.
The offset portion 21A is formed on the liner 23 alone by machining such as crowning, and the liner 23 is disposed in the recess 3C of the end plate 3A. The liner 23 is integrated with the end plate 3A by an appropriate method. For example, the liner 23 is arranged inside the mold of the end plate 3A, and the liner 23 can be integrated by casting. Further, the liner 23 can be fastened to the end plate 3A.

Prior to the start of use, an operation by the offset portion 21A formed on the wall 21 will be described.
As shown in FIG. 5A, when the first key 11 is tilted with respect to the wall 21, the side surface 11S of the first key 11 is placed on the gently curved offset portion 21A (FIG. 5B). Because of the contact, the first key 11 and the wall 21 (liner 23) of the key groove 20 can be brought into surface contact, and the sliding friction is suppressed even at the edge of the outer peripheral end 20A of the key groove 20.
Therefore, the wall 21 of the key groove 20 and the side surface 11S of the first key 11 are immediately adapted to each other without abrasion peculiar to the initial stage of use, and slide stably with low friction.

In the present embodiment, the surface roughness Ra of the wall 31 of the key groove 30 (FIG. 6) also simulates the surface state of the wall 41 (FIG. 7) worn by use. Has a surface roughness Ra of 0.2 μm or less.
Since the surface roughness Ra of the existing wall 41 (FIG. 7) exceeds 0.2 μm, when the unused scroll compressor 1 starts to be used, the sliding friction between the second key 12 and the wall 41 occurs. The surface roughness Ra of the wall 41 gradually decreases from the initial state. Thereafter, when the side of the wall 41 of the key groove 30 and the side surface of the second key 12 are adapted, the surface roughness Ra of the wall 41 is stabilized. At this time, the surface roughness Ra of the wall 41 is 0.2 μm or less.
The surface roughness Ra of the wall 31 (FIG. 6) of the key groove 30 of the present embodiment is set to 0.2 μm or less in advance based on the above-described wall 41 wear process.
The surface roughness Ra of the side surface of the key 12 that slides on the wall 31 of the key groove 30 is set to 0.2 μm or less, which is the same as the case where the surface roughness Ra of the wall 31 is set to 0.2 μm or less. Although the effect can be obtained, the surface roughness Ra of the wall 31 of the key groove 30 is set to 0.2 μm or less in consideration of processing cost and labor.

  The wall 31 is preferably formed by a liner 28 separate from the base material of the keyway 30. By polishing the liner 28 alone, the surface (sliding surface) of the liner 28 forming the wall 31 can have a predetermined surface roughness (Ra).

  Prior to the start of use of the scroll compressor 1, if the surface roughness Ra of the wall 31 is set to 0.2 μm or less, the wall 31 of the key groove 30 and the side surface of the second key 12 quickly adapt, and the surface roughness is reduced. Because of its small size, solid contact can be reduced even with a thin oil film. Therefore, a large amount of wear peculiar to the initial stage does not occur, and the wall 31 of the key groove 30 and the side surface of the second key 12 slide stably with low friction.

As described above, the first key 11 and the key groove 20 of the Oldham link 10 are formed with the offset portion 21A, and the second key 12 and the key groove 30 are set with the surface roughness Ra. Can be suppressed. Through this, wear of the keys 11 and 12 of the Oldham link 10 and the walls 21 and 31 of the key grooves 20 and 30 can be reduced, and power loss due to friction can be suppressed.
According to the present embodiment, even under severe lubrication conditions, the wear of the keys 11, 12 and the key grooves 20, 30 can be suppressed by forming the offset portion 21A and setting the surface roughness Ra. Therefore, when the low-speed operation is continued, it is possible to eliminate the restriction on the operation such as increasing the rotation speed in order to prevent a shortage of the lubricating oil.

Incidentally, since it is difficult to sufficiently supply the lubricating oil, it is preferable that a coating is formed on the sliding portion of the Oldham link 10 which is likely to be subjected to severe lubrication conditions using a solid lubricant.
For example, using a solid lubricant or the like in which polytetrafluoroethylene (PTFE) powder is dispersed in an epoxy resin, a polyimide resin, or the like, the surfaces of the keys 11 and 12 and the surfaces of the walls 21 and 31 of the key grooves 20 and 30 are used. (A surface of the liner). Illustration of the coating is omitted.
When a coating made of a solid lubricant is formed on the offset portion 21A, it is preferable to machine the wall 21 with an offset larger than a desired offset in consideration of the thickness of the coating. In that case, the final offset amount is determined by the surface of the film made of the solid lubricant.
In the case where a solid lubricant film is formed on a portion where the surface roughness Ra is set to 0.2 μm or less, the surface roughness Ra of the solid lubricant film on the surface of the base material is processed to 0.2 μm or less. I do. For example, the solid lubricant film can be polished by mechanical polishing by spraying a grinder or abrasive grains, or by chemical polishing in which the film is dissolved using a chemical material.

  In the present embodiment, since the presence of the offset portion 21A and the setting of the surface roughness Ra do not cause significant wear in the initial stage of use, the coating of the solid lubricant applied to the walls 21 and 31 is worn away. Survive without leaving. The coating can be maintained to ensure wear resistance.

The coating of the solid lubricant can be formed on all of the keys 11 and 12 and the key grooves 20 and 30 or on a part selected according to lubrication conditions and the like.
Further, since the Oldham link 10 slides on the end plate 3A and the bearing 6 while restricting the rotation of the orbiting scroll 3, the coating of the solid lubricant is applied to the Oldham link 10 in order to improve the lubricity of the Oldham link 10 as a whole. May be applied over the entire sliding surface.

[Modification of First Embodiment]
In addition to forming the offset portion 21A (FIG. 5B), it is preferable to set the surface roughness Ra of the wall 21 of the key groove 20 to 0.2 μm or less.
In order to appropriately determine the surface roughness Ra, it is preferable to perform the durability test while varying the surface roughness Ra.
FIG. 8 plots the relationship between the wear depth (amount of wear) at the outer peripheral end of the key 11 and the surface roughness Ra of the wall 21 after performing the durability test with black diamonds (◆). . The wear depth is an average value of a plurality of measured values. The amount of wear and the surface roughness Ra of the wall 21 of the keyway 20 correspond to the amount of wear and the surface roughness Ra of the key 11, respectively.
As shown in FIG. 8, when the surface roughness Ra is small, the amount of wear after the durability test decreases.
Taking into account the dispersion of the measured values in a plurality of tests (the measured wear depth exceeding the average is indicated by a straight line), the surface roughness Ra of the wall 21 is 0.2 μm in order to keep the wear depth below the allowable wear depth. Must be:

  Prior to the start of use, if the wall 21 is provided with the offset portion 21A and the surface roughness Ra of the wall 21 is 0.2 μm or less, the wear can be reduced more sufficiently.

FIG. 9A shows another modification of the first embodiment.
The wall 21 of the key groove 20 is provided with an offset portion 21B located near the inner peripheral end 20B in addition to the offset portion 21A located at the outer peripheral end 20A.
It is preferable that the offset portion 21B is gradually offset with respect to the reference surface 210 toward the inner peripheral end portion 20B.
Like the offset unit 21A, the offset unit 21B is illustrated with an exaggerated offset amount.

There is no shaded portion in FIG. The surface of the offset portion 21A is indicated by 21S, and the surface of the offset portion 21B is indicated by 21S '.
The shape of each surface 21S, 21S 'of the offset portions 21A, 21B simulates the surface shape of the wall 21 worn by use.

As shown in FIG. 9B, the wedge effect accompanying the inflow of the lubricating oil between the first key 11 and the wall 21 causes the first key 11 to move forward and backward in both directions. An oil film 100 is formed between the key 11 and the wall 21.
Here, at both ends of the wall 21 in the sliding direction, the displacement speed of the first key 11 is slow, so that it is difficult to sufficiently obtain the wedge effect, so that the oil film 100 is hardly formed. Then, at both ends of the wall 21, the sliding friction with the first key 11 inclined with respect to the wall 21 increases the amount of wear as compared with the central portion of the wall 21. Offset portions 21A and 21B are formed near the side end 20A and the inner peripheral end 20B.

The offset amount Of of the offset portion 21A with respect to the reference surface 210 corresponds to the amount of wear on the outer peripheral side (radially outer side) of the wall 21, and the offset amount Of 'of the offset portion 21B with respect to the reference surface 210 is within the wall 21. It corresponds to the amount of wear on the circumferential side (radially inside).
In the configuration shown in FIG. 9A, the offset amount Of of the offset portion 21A is larger than the offset amount Of ′ of the offset portion 21B based on the fact that the key groove 20 is particularly easily worn on the open end side (20A side). are doing.

  According to the configuration shown in FIGS. 9A and 9B, since the offset portions 21A and 21B are formed in anticipation of wear due to use, wear can be reduced without causing significant wear peculiar to the initial stage. Can be.

Prior to use, forming an offset portion simulating wear can also be applied to the wall 31 of the keyway 30 that slides with the second key 12 (FIG. 6).
The position and offset amount of the offset portion formed on the wall 31 can be appropriately determined based on the stroke of the second key 12 and sliding conditions.
For example, in a region of the wall 31 corresponding to the sliding range Rg2 of the second key 12 (FIG. 4), an offset portion can be formed so as to be symmetric with respect to the center of the range Rg2.

[Second embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS.
The second to fifth embodiments are characterized by a structure for positioning a liner in a keyway. The second to fifth embodiments can be appropriately combined.
Hereinafter, a liner arranged in the key groove 20 in which the first key 11 slides will be described as an example, but a liner arranged in the key groove 30 in which the second key 12 slides will also be described below. Configuration can be applied.

As shown in FIG. 10A, the surface of the liner 24 arranged flush with the inner peripheral portion 201 of the keyway 20 has a crowning process for forming the offset portion 21A and the offset portion 21B, and has a surface roughness of 0. At least one of the machining to be 2 μm or less is performed. The illustration of the offset unit is omitted.
The above also applies to the liners (described later) shown in FIGS.

  In the configuration shown in FIG. 10A, the convex portion 241 provided on the liner 24 is fitted into the concave portion 211 formed on the inner peripheral portion 201 of the key groove 20. The concave portion 211 is recessed from the surface 3E of the liner 24 where the plate-shaped main body 240 is arranged. The protrusion 241 of the liner 24 is fitted between the walls 211A and 211B that are separated in the sliding direction in the recess 211.

  In this specification, the direction in which the first key 11 slides along the radial direction of the rotating shaft 5 is referred to as a “sliding direction”. The direction in which the second key 12 slides along the radial direction of the rotating shaft 5 is also referred to as the “sliding direction”.

  In the configuration shown in FIG. 10A, the concave portion 211 and the convex portion 241 make the liner 24 and the inner peripheral portion 201 of the keyway 20 fit into each other unevenly, whereby the liner 24 is turned in the sliding direction. 3 is positioned. Therefore, it is possible to prevent the liner 24 from being displaced or detached from the inner peripheral portion 201 of the key groove 20 in the sliding direction.

In addition to the configuration shown in FIG. 10A, for example, the liner 24 can be positioned in the key groove 20 by the concave and convex fitting as shown in FIGS. 10B and 10C.
In FIG. 10B, the protrusion 241 of the liner 24 is located radially outward as compared with FIG. 10A. Others are the same as FIG.
In FIG. 10C, concave portions 212 are formed near the outer peripheral end portion 20 </ b> A and the inner peripheral end portion 20 </ b> B of the inner peripheral portion 201 of the keyway 20, respectively. Two projections 251 and 251 projecting rearward from the plate-shaped main body 250 of the liner 25 are fitted.

  In the configurations shown in FIGS. 10A to 10C, the main portions 240 and 250 of the liners 24 and 25 extend to the open ends (outer peripheral end portions 20 </ b> A) of the key grooves 20, so that the key grooves are provided. The sliding friction with the first key 11 at the edge 20 can be reduced.

[Third embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 11, the liner 26 of the third embodiment is formed in a U-shape, and is arranged over the entire inner peripheral portion 201 of the keyway 20.
The liner 26 connects the plate-like portion 261 on which the first key 11 slides, the plate-like portion 262 facing the plate-like portion 261, and the plate-like portions 261 and 262 at the inner peripheral end 20 </ b> B of the key groove 20. And a connecting portion 263 to be connected.

In the configuration shown in FIG. 11, the liner 26 is positioned in the key groove 20 without forming a convex portion or a concave portion in the liner 26 and the key groove 20.
Since the width of the liner 26 in the direction connecting the plate portions 261 and 262 is set to be larger than the width of the key groove 20, the liner 26 bends in a compressed state inside the key groove 20, and It is fixed in the keyway 20.
Therefore, it is possible to prevent the liner 26 from being displaced from the inner peripheral portion 201 of the key groove 20 in the sliding direction or the width direction of the liner 26, and the liner 26 from being detached from the key groove 20.

The second embodiment and the third embodiment can be appropriately combined.
In FIG. 12A, the convex portion 264 formed on the U-shaped liner 26 fits into the concave portion 212 formed on the inner peripheral portion 201 of the key groove 20.
The configuration of FIG. 12B is the same as that of FIG. 12A, except that the liner 26 is inserted into a concave portion 213 formed in the inner peripheral portion 201 of the key groove 20 in a region where the first key 11 slides. The projection 265 is fitted.
Further, in FIG. 13, the convex portion 214 formed on the inner peripheral portion 201 of the key groove 20 fits into the concave portion 266 formed on the U-shaped liner 26.
In the configurations shown in FIGS. 12 (a), 12 (b) and 13 respectively, it is not necessary to fix the liner 26 in the keyway 20 by elastic force or by interference fit. According to the concave and convex fitting between the U-shaped liner 26 and the inner peripheral portion 201 of the key groove 20, the liner 26 is shifted from the inner peripheral portion 201 of the key groove 20 in the sliding direction or the width direction, The separation of the liner 26 from the groove 20 can be prevented.

[Fourth embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIGS.
In the configuration shown in FIG. 14A, a liner groove 29 for receiving the peripheral edge 271 of the liner 27 is formed in the bottom 202 of the key groove 20.
The entire peripheral edge 271 of the U-shaped liner 27 fits inside the U-shaped liner groove 29 formed at the base of the inner peripheral portion 201 of the key groove 20.
According to this configuration, the liner 27 fits into the key groove 20 of the orbiting scroll 3 in both the sliding direction and the width direction by the concave and convex fit between the liner groove 29 (recess) and the peripheral edge 271 (projection) of the liner 27. Positioned.

As shown in FIG. 14B, a J-shaped liner 27 'can be employed.
The liner 27 ′ is connected to a plate-shaped portion 291 arranged in the region of the inner peripheral portion 201 where the first key 11 slides, and to the inner peripheral end of the plate-shaped portion 291, and to the arc-shaped inner peripheral end 20 B. And a curved portion 292 that is curved along.
By fitting the plate-shaped portion 291 into the linear portion of the liner groove 29, the liner 27 ′ is positioned in the key groove 20 in the plate thickness direction, and the curved portion 292 is fitted into the curved portion of the liner groove 29, The liner 27 'is positioned in the keyway 20 in the sliding direction.

  The configuration of the fourth embodiment can be used for positioning the liner 28 (FIG. 6) on which the second key 12 slides. In that case, for example, the periphery of the liner 28 is fitted into a liner groove formed at the bottom of the key groove 30. Then, the liner 28 is positioned in both the plate thickness direction and the sliding direction by the concave and convex fit between the peripheral edge of the liner 28 and the liner groove.

[Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIG.
The liner 50 shown in FIG. 15 has a bottom 51A disposed on the bottom 202 of the key groove 20 and a U-shaped wall 51B rising from the bottom 51A and disposed on the inner peripheral portion 201 of the key groove 20. ing.
The bottom 51 </ b> A of the liner 50 is made larger than the width of the bottom 202 of the key groove 20, and is pressed into the bottom 202 of the key groove 20 to form the bottom surface of the key groove 20.
At least one of a crowning process for forming an offset portion (not shown) and a machining process for reducing the surface roughness to 0.2 μm or less is performed on the inner surface (sliding surface) of the wall portion 51B.
The wall portion 51B may be formed in a J shape like the liner 27 'in FIG. 14B, or may be formed in a plate shape like the liner 23 shown in FIG.

  Since the bottom portion 51A is press-fitted and fixed in the key groove 20, it is possible to prevent the liner 50 from being displaced from the inner peripheral portion 201 of the key groove 20 in the sliding direction or the width direction, and preventing the liner 50 from being detached from the key groove 20. it can.

  The configuration of the fifth embodiment can be used for positioning the liner 28 (FIG. 6) on which the second key 12 slides.

[Sixth embodiment]
Next, a sixth embodiment of the present invention will be described with reference to FIG.
In the sixth embodiment, a liner whose displacement is allowed in the key sliding direction is interposed between the key and the wall of the keyway.
FIG. 16 shows a keyway 30 in which the second key 12 is arranged.
A plate-shaped liner 52 that forms the wall 31 that slides with the second key 12 is disposed in the key groove 30.
The liner 52 is housed in a liner housing 53 formed on the bearing 6.
Since the size of the liner housing 53 is larger than the size of the liner 52 in the sliding direction, there is a gap Sp in the liner housing 53 that allows the displacement of the liner 52 in the sliding direction of the second key 12. .
When the second key 12 comes into contact with the liner 52 (wall 31) and is displaced in the sliding direction while holding the liner 52 by frictional force, the liner 52 is also displaced in the liner accommodating portion 53 (see the arrow).

According to the sixth embodiment, since the second key 12 reciprocates with the liner 52, the distance by which the second key 12 and the liner 52 slide relative to each other can be reduced. The wear of the key 12 and the liner 52 can be reduced.
The rear surface of the liner 52 slides on the inner peripheral portion 301 of the key groove 30, but the frictional force is proportionally distributed between the second key 12 and the liner 52 and between the liner 52 and the inner peripheral portion 301. Wear of each of the two keys 12, the liner 52, and the inner peripheral portion 301 (bearing 6) is suppressed.

In order to prevent the key 12 from protruding from the end of the liner 52, as shown in FIG. 16, the stroke of the key 12 is d, the dimension of the liner housing 53 which is the movable range of the liner 52 is Ln, If the length of the gap is defined as Sp, the following relationship must be satisfied.
Ln / 2−d / 2> Sp
According to this relationship, the liner 52 can be displaced together with the key 12 while holding the key 12 between the left end and the right end of the liner 52.

  In the sixth embodiment, it is not always necessary to form an offset portion in the liner 52 or set the surface roughness of the liner 52 to 0.2 μm or less. As in the case of the liner 23 and the like described above, if at least one of the crowning process for forming the offset portion and the machining process for reducing the surface roughness to 0.2 μm or less is also performed on the liner 52, the wear of the liner 52 is reduced. It can further contribute to reduction.

[Seventh embodiment]
Next, a seventh embodiment of the present invention will be described with reference to FIGS.
In the seventh embodiment, the liner is configured to swing according to the position of the key.
FIG. 17A shows a key groove 20 in which the first key 11 is arranged.
A plate-like liner 54 that forms the wall 21 that slides with the first key 11 is arranged in the key groove 20.
The liner 54 is accommodated in a concave portion 55 formed in the orbiting scroll 3.
On the wall of the concave portion 55 located on the back side of the liner 54, a support portion 551 projecting in an arc shape in plan view is formed. The support portion 551 is located near the inner peripheral end 20 </ b> B of the wall of the concave portion 55. The liner 54 supported by the support portion 551 can swing within the range of the clearance CL between the liner 54 and the wall of the concave portion 55.

  FIG. 17B shows an example in which the support portion 541 is formed not on the concave portion 55 but on the back side of the liner 54. The liner 54 supported by the concave portion 55 by the support portion 541 can swing within the range of the clearance CL between the liner 54 and the wall of the concave portion 55.

When the first key 11 reciprocates, as shown in FIG. 18, the liner 54 swings (falls) at an angle following the attitude of the first key 11. In both the forward path and the return path of the first key 11, the outer end of the liner 54 is formed with the concave portion 55 at an angle parallel to the axis of the key groove 20 with the support portion 541 (or 551) as a fulcrum. Swing up to the angle of contact with the wall.
As a result, the side surface 11S of the first key 11 comes into surface contact with the liner 54, so that the first key 11 slides on the surface of the liner 54 stably with low friction.
According to the seventh embodiment, since the liner 54 swings and follows the posture of the first key 11, the sliding friction between the first key 11 and the liner 54 can be suppressed. 54 can be reduced.

  In the seventh embodiment, it is not always necessary to form an offset portion in the liner 54 or set the surface roughness of the liner 54 to 0.2 μm or less. As in the case of the liner 23 and the like described above, if at least one of the crowning process for forming the offset portion and the machining process for reducing the surface roughness to 0.2 μm or less is also performed on the liner 54, the wear of the liner 54 is reduced. It can further contribute to reduction.

[Eighth Embodiment]
Next, an eighth embodiment of the present invention will be described with reference to FIG.
In the eighth embodiment, lubricating oil supplied around the eccentric pin 5A through an oil supply path 5C (FIG. 2) inside the rotary shaft 5 is supplied to the sliding surface through the inside of the liner.
As shown in FIG. 2, the eccentric pin 5A is connected to the inside of the boss 3F of the orbiting scroll 3 via a bearing 5B. The eccentric pin 5A, the bearing 5B, and the boss 3F are arranged in a recess 6C formed around the rotation shaft 5 in the bearing 6.
The inside of the recess 6C is an oil reservoir in which lubricating oil is retained. A pressure difference is provided between the atmosphere inside the recess 6C and the atmosphere outside the recess 6C, and the lubricating oil in the recess 6C is supplied to the outside of the recess 6C according to the pressure difference. It has become.

  Hereinafter, a liner arranged in the key groove 20 in which the first key 11 slides will be described as an example, but a liner arranged in the key groove 30 in which the second key 12 slides will also be described below. Configuration can be applied.

The liner 56 of this embodiment is a member that is assembled to the orbiting scroll 3 and forms a part of the keyway 20, as shown in FIGS. 19A and 19B.
The surface of the liner 56 forming the wall 21 on which the first key 11 slides is processed to form an offset portion or to reduce the surface roughness to 0.2 μm or less.

As shown in FIGS. 19B and 19C, an oil path 57 through which lubricating oil flows is formed by the key groove 20 and the liner 56.
The oil path 57 includes a first path 571 extending along the sliding direction on the back side of the liner 56, and a sliding surface (wall 21) of the liner 56 extending from the first path 571 in the thickness direction of the liner 56. And a plurality of second paths 572 that reach.

As shown in FIG. 19B, the first path 571 is formed between a groove 571C formed on the back surface of the liner 56 and the wall of the recess 3C where the liner 56 is arranged (FIG. 19A). Have been.
The start end 571A of the first path 571 communicates with the inside of the recess 6C (FIG. 2) where the lubricating oil is stored.
The plurality of second paths 572 are arranged at intervals in the sliding direction between the start end 571A and the end 571B of the first path 571, and all of them are open to the surface of the liner 56.

During operation of the scroll compressor 1, the lubricating oil in the recess 6C is forcibly applied to the sliding surface between the first key 11 and the key groove 20 (liner 56) through the oil path 57 based on the pressure difference between the inside and the outside of the recess 6C. Supplied to The first key 11 floats from the surface of the liner 56 by the pressure of the lubricating oil ejected from each of the second paths 572 opened on the surface of the liner 56 on which the first key 11 slides, and the first key 11 and the liner 56 An oil film is formed between the two.
According to the present embodiment, the supply amount of the lubricating oil to the key groove 20 is increased by the lubricating oil flowing through the oil path 57, and the first key 11 and the wall of the key groove 20 which float by the lubricating oil ejected from the oil path 57. 21, a thick oil film is formed. Therefore, since solid contact is reduced, it is possible to contribute to reduction in wear of the first key 11 and the wall 21 (liner 56) of the key groove 20.
According to the eighth embodiment, in addition to the offset portion being formed in the liner 56 and the surface roughness being set to 0.2 μm or less, the wear to the sliding surface through the oil path 57 is reduced. It can be reduced more sufficiently.

The oil path 57 can be appropriately modified as long as the inside of the recess 6C and the wall 21 of the key groove 20 communicate with each other.
For example, the groove forming the first path 571 may be formed not on the liner 56 but on the wall of the concave portion 3C located on the back surface of the liner 56.
Further, as shown in FIG. 19D, the first path 571 can be formed inside the liner 56.

  The configuration of the oil path 57 in the eighth embodiment is achieved without assuming a process for forming an offset portion in the liner 56 or a process for reducing the surface roughness of the liner 56 to 0.2 μm or less. That is, oil supply to the sliding surface through the oil path 57 can contribute to reduction of wear.

In addition to the above, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate without departing from the gist of the present invention.
In addition to the scroll compressor, the Oldham link according to the present invention revolves the rotational motion of a member that is coupled eccentrically with respect to the rotation shaft and that is rotated with the rotation shaft while restricting the rotation of the member. The present invention can be applied to a device provided with a mechanism for converting into a turning motion.

Reference Signs List 1 scroll compressor 2 fixed scroll 2P discharge port 3 orbiting scroll (body)
3A End plate 3B Outer edge 3C Recess 3E Surface 3F Boss 4 Motor 4A Stator 4B Rotor 5 Rotating shaft 5A Eccentric pin 5B Bearing 5C Oil supply path 6 Bearing (main body)
6A Thrust surface 6C recess (oil pool)
7 Bearing 8 Housing 10 Oldham Link 11 First Key 12 Second Key 13 Connecting Portion 20 Keyway 20A Outer End 20B Inner End 21 Wall 21A Offset 21B Offset 21S Surface 23-27 Liner 28 Liner 29 Liner Groove 30 Key groove 30A Outer end 30B Inner end 31 Wall 40 Key groove 40A Outer end 40B Inner end 41 Wall 50 Liner 51A Bottom (liner bottom)
51B Wall (Liner wall)
52 liner 53 liner housing portion 54 liner 55 recess 56 liner 57 oil path 91 suction pipe 92 discharge pipe 100 oil film 101 pump 131 one surface 132 other surface 201 inner peripheral portion 202 bottom 210 reference surface 211 recess 211A, 211B wall 212 recess 213 recess 214 Convex part 240 Main part 241 Convex part 250 Main part 251 Convex part 261, 262 Plate part 263 Connecting part 264 Convex part 265 Convex part 266 Concave part 271 Peripheral edge 291 Plate part 292 Curved part 541 Support part 551 Support part 571 First path 571C Groove 571A Start end 571B End end 572 Second path CL Clearance D1 Direction D2 Direction R Compression chambers Rg1, Rg2 Range Sp Gap

Claims (10)

A fixed scroll fixed to the housing,
An orbiting scroll that is coupled eccentrically to the rotation axis and revolves around the fixed scroll;
A bearing fixed to the housing and supporting the orbiting scroll;
An Oldham link interposed between the orbiting scroll and the bearing to regulate the rotation of the orbiting scroll,
The Oldham Link,
A first key that slides in a radial direction of the rotation shaft with respect to a wall of a keyway provided in the orbiting scroll;
A second key that slides in a radial direction of the rotating shaft with respect to a wall of another key groove provided in the bearing,
Assuming a flat reference surface on the wall of the keyway,
Possess progressively offset portion being offset with respect to the reference surface toward the at least one of the outer peripheral side end portion and the inner circumferential end of the key groove in the wall,
At least a part of the inner peripheral portion of the keyway including the offset portion, or the entirety of the inner peripheral portion is separate from the main body that is the orbiting scroll or the bearing, and the first key or the first It is a liner that can make surface contact with 2 keys,
The offset unit,
The shape is given so that the increasing rate of the offset amount with respect to the reference plane gradually increases toward the outside or inside in the radial direction.
A scroll compressor, characterized in that: The surface roughness Ra of the sliding surface of the wall including the surface of the offset portion is:
Prior to the start of use of the Oldham link, it is 0.2 μm or less,
The scroll compressor according to claim 1, wherein: The liner is
By being unevenly fitted to the main body located on the back side, the main body is positioned in a sliding direction in which the first key or the second key slides.
The scroll compressor according to claim 1 or 2 , wherein: The liner is
Formed in a substantially U-shape,
The scroll compressor according to any one of claims 1 to 3, wherein: At the bottom of the keyway,
A liner groove (29) for receiving an edge of the liner is formed;
The scroll compressor according to any one of claims 1 to 4 , wherein: The liner is
Forming a bottom surface of the keyway, a liner bottom pressed into the main body,
A liner wall that rises from the liner bottom and includes the offset portion.
The scroll compressor according to any one of claims 1 to 5 , wherein: A coating using a solid lubricant is formed on the surface of the liner,
The scroll compressor according to any one of claims 1 to 6, wherein: In the body,
A liner housing portion that houses the liner and that allows displacement of the liner in a sliding direction that is a direction in which the first key or the second key slides;
The scroll compressor according to any one of claims 1 to 7 , wherein: The liner is
It is swingably supported by the main body located on the back side,
The scroll compressor according to any one of claims 1 to 8 , wherein: At least the liner of the liner and the inner peripheral portion of the key groove,
An oil path is formed that communicates with an oil sump present around a joint between the rotary shaft and the orbiting scroll and supplies lubricating oil from the oil sump to the wall of the key groove.
The scroll compressor according to any one of claims 1 to 9 , wherein:

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