JP2012082714A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a highly reliable scroll compressor by reducing wear of a crowning shape part of an eccentric shaft part.SOLUTION: The scroll compressor comprises an electric motor, a main shaft 6 connected to the electric motor so as to be rotated, an eccentric shaft part 8 provided on a top end surface 6A of the main shaft 6 at a position D off the axis C of the main shaft 6, a slider 7 having a long hole 15 for storing the eccentric shaft part 8 provided slidably with the eccentric shaft part 8, a first slider plate 17 disposed between the eccentric shaft part 8 and the inner surface 19 of the long hole 15 receiving contact force Fn from the eccentric shaft part 8 at the time of rotating the main shaft 6, a storage groove part 16 formed on the inner surface 19 of the long hole 15 for storing the first slider plate 17, a swing scroll pivoted rotatably on the slider 7, and a fixed scroll for forming a compression chamber with respect to the swing scroll. A second slider plate is disposed slidably between the first slider plate 17 and the eccentric shaft part 8.

Description

  The present invention relates to a scroll compressor used for an air conditioner or a refrigerator.

  Conventionally, as this scroll compressor, what was described in the following patent documents 1 and 2, for example is known. The scroll compressors disclosed in these publications include a hermetic compressor main body, a fixed scroll fixed in the compressor main body, and a fixed scroll having a swing center eccentric to the center of the fixed scroll. The swing scroll that forms the compression chamber, the stator and the rotor that constitute the electric motor, the main shaft that is connected to the electric motor and driven to rotate, and the tip end surface of the main shaft is provided at a position that is eccentric from the axis of the main shaft. An eccentric shaft portion, a long hole that slidably accommodates the eccentric shaft portion, a slider that supports the orbiting scroll for revolving motion, and a length that receives contact force from the eccentric shaft portion when the main shaft rotates A first slider plate that is slidably interposed between the inner surface of the hole and the eccentric shaft portion, and an accommodating groove portion that is formed on the inner surface of the elongated hole and accommodates the first slider plate. Fluid is pressurized by revolution Inhalation to be discharged into the chamber. In this scroll compressor, a substantially rectangular elongated hole is formed in the central portion of the slider in plan view, and the eccentric shaft portion is formed in a substantially rectangular cross section so that the eccentric shaft portion is slidably accommodated in the elongated hole. ing. With such a configuration, the slider slides only in a certain direction on a surface orthogonal to the axial direction of the main shaft.

  Here, the role of the slider will be described. When the operation of the scroll compressor starts, a force accompanying the compression of the refrigerant and a radial force (mainly centrifugal force) act on the center of the slider. The radial force has the effect of increasing the crank radius and attempts to null the radial gap between the scroll teeth of each scroll. As described above, the long hole of the slider is substantially rectangular. However, a groove is formed on the inner surface of the long hole that is mainly in contact with the eccentric shaft, and the slider plate is accommodated in the groove. The eccentric shaft portion is brought into contact with the eccentric shaft portion. Further, a convex curved crowning portion is provided on the contact load surface in contact with the slider plate in the eccentric shaft portion. This is a configuration to keep the slider and the orbiting scroll bearing in parallel even if the main shaft is deformed by bearing load, and the longitudinal cross-sectional shape of the contact load surface of the crowning shape part is processed into an arc shape. The slider and the orbiting scroll bearing are kept parallel.

Next, the operation will be described. The main shaft is rotated by the drive of the electric motor, whereby the orbiting scroll revolves around the axis of the main shaft while being guided by the Oldham coupling. Fluid is sucked into the compression chamber from the suction pipe on the side of the compressor body, moves while being compressed toward the spiral center of the fixed scroll by the revolution of the orbiting scroll, and is discharged out of the compressor body through the discharge pipe. . At that time, in order to prevent the compressed fluid from leaking from the compression chamber, the orbiting scroll revolves while being pressed against the fixed scroll. In addition, centrifugal force is generated by the revolution of the orbiting scroll, and the contact load surface of the long hole of the slider in which the eccentric shaft portion is accommodated is subjected to contact force as a combined force of the above pressing force and centrifugal force. It will be. Furthermore, continuous vibration caused by the electric motor is generated on the contact load surface of the long hole. In addition, when there is no slider plate between the eccentric shaft and the slider, the eccentric shaft and the slider are repeatedly adhered and peeled due to the revolution of the orbiting scroll during fluid compression. Wear occurs, and as a result, the contact load surface of the long hole of the slider wears. Conventionally, in order to suppress this fretting wear, the surface roughness between the eccentric shaft portion and the slider is smaller than that of the eccentric shaft portion and the inner wall of the long hole of the slider, and has a hardness equal to or higher than that of the slider. One slider plate is interposed, and the slider plate and the eccentric shaft portion are slid to suppress the wear of the slider itself.

JP 2003-129969 A JP 2007-64058 A

  In the conventional scroll compressor described above, the crowned shape portion of the eccentric shaft portion and the steel slider plate slide in the long hole of the slider during operation. Since this sliding is a sliding with a minute width within the sum of the shape tolerance of the orbiting scroll and the fixed scroll (tolerance with respect to the deviation of the form) and the assembly tolerance, it is difficult to form an oil film at the sliding portion. As a result, there is a problem that the crowning shape portion of the eccentric shaft portion having a lower hardness than the slider plate is worn. In particular, in scroll compressors used in low temperature applications where the performance of the lubricant is likely to deteriorate, and scroll compressors using HFC refrigerants or CO2 refrigerants that are operated at low temperatures and high pressures to increase the contact load, eccentric shaft portions The crowning shape portion of this becomes more easily worn. When wear of the crowning shape portion of the eccentric shaft portion occurs, when the eccentric shaft portion is deformed by bending due to a load (consisting of a swinging scroll centrifugal force, etc.) received from the slider, the slider and the swing scroll The parallelism with a bearing cannot be maintained, but the problem that the reliability of a compressor falls arises.

  The present invention has been made to solve the above-described problems, and an object thereof is to obtain a highly reliable scroll compressor by reducing wear of the crowning shape portion of the eccentric shaft portion.

A scroll compressor according to the present invention includes an electric motor, a main shaft coupled to the electric motor and driven to rotate, an eccentric shaft portion provided at a position eccentric from the axis of the main shaft on the tip surface of the main shaft, and an eccentric shaft portion. A first slot is provided between the inner surface of the elongated hole that receives the contact force from the eccentric shaft portion when the main shaft rotates and the eccentric shaft portion. A slider plate, an accommodation groove formed on the inner surface of the elongated hole and accommodating the first slider plate, an orbiting scroll pivotally supported by the slider and revolving around the axis of the main shaft, and a compressor container In a scroll compressor, which includes a fixed scroll that forms a compression chamber between the fixed scroll and the swing scroll, and that sucks and discharges fluid into the compression chamber by the revolution of the swing scroll, the first slider plate and the eccentric shaft portion The second slur between It is characterized in that the slidably interposed a Dapureto.

  In the scroll compressor according to the present invention, the second slider plate is slidably interposed between the first slider plate and the eccentric shaft portion disposed in the long hole of the slider, so that the eccentric shaft portion and the slider are connected to each other. Two slider plates are interposed between the inner surfaces of the long holes. Thereby, sliding occurs in the slider sliding direction between the first and second slider plates. Therefore, sliding between the second slider plate and the crowning shape portion of the eccentric shaft portion and the accompanying fretting wear of the crowning shape portion can be suppressed, and the wear of the crowning shape portion can be reduced. It becomes possible. As a result, even when the eccentric shaft portion bends and deforms due to the load received from the slider, the slider and the bearing of the orbiting scroll can be kept parallel, and a highly reliable scroll compressor can be provided.

It is a longitudinal section of a scroll compressor concerning each embodiment of this invention. It is a partial expanded cross-sectional view of the eccentric shaft part, slider plate, and slider of the scroll compressor according to Embodiment 1 of the present invention. It is a partial expanded longitudinal cross-sectional view of the eccentric shaft part of the scroll compressor which concerns on Embodiment 1 of this invention, a slider plate, and a slider. It is a partial expanded longitudinal cross-sectional view of the eccentric shaft part of the scroll compressor which concerns on Embodiment 2 of this invention, a slider plate, and a slider. It is an enlarged plan view of the main axis | shaft and eccentric shaft part of the scroll compressor which concerns on Embodiment 2 of this invention. It is an enlarged plan view of a main shaft, an eccentric shaft portion, and two slider plates of a scroll compressor according to Embodiment 2 of the present invention. It is a partial expanded longitudinal cross-sectional view of the eccentric shaft part and slider plate of the scroll compressor which concerns on Embodiment 3 of this invention. It is a partial expanded cross-sectional view of the eccentric shaft part and slider plate of the scroll compressor which concerns on Embodiment 3 of this invention. It is a partial expanded longitudinal cross-sectional view for showing the eccentric shaft part of the scroll compressor which concerns on Embodiment 4 of this invention, a slider plate, and the surface roughness of a slider.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view of a scroll compressor according to each embodiment of the present invention, and FIG. 2 is a partially enlarged transverse sectional view of the eccentric shaft portion, slider plate, and slider of the scroll compressor according to embodiment 1 of the present invention. 3 is a partially enlarged longitudinal sectional view of the eccentric shaft portion, slider plate, and slider of the scroll compressor according to Embodiment 1 of the present invention.
In each figure, the scroll compressor 1 has a hermetic compressor container 9, a fixed scroll 2 fixed to the upper part of the compressor container 9, and a swing center eccentric to the center of the fixed scroll 2. The swinging scroll 3 that forms the compression chamber 24 with the fixed scroll 2, the stator 4 and the rotor 5 that constitute the electric motor 23, and the main shaft 6 that is rotated by being attached with the rotor 5 of the electric motor 23. And the slider 7 mounted in the bearing 28 on the lower surface of the orbiting scroll 3 to make the orbiting scroll 3 revolve, and the shaft 6 on the front end surface 6A of the main shaft 6 so that the slider 7 is eccentric with respect to the main shaft 6. The eccentric shaft portion 8 erected at a position eccentric from the center C (the eccentric D position), the suction pipe 10 for introducing the refrigerant gas into the compressor container 9, and the refrigerant gas compressed in the compression chamber 24 Discharge pipe for discharging to the outside 1, an upper frame 12 fixed to the fixed scroll 2 with bolts or the like and slidably supporting the swing scroll 3, and oil accumulated at the bottom of the compressor container 9 through an oil supply passage 6 </ b> B in the main shaft 6. A positive displacement oil pump 13 sucked up by the slider 7 is provided.

The positive displacement oil pump 13 is attached to a lower frame 25 fixed to the lower part in the compressor container 9. A central plane portion of the lower frame 25 is a lower bearing portion 26 that thrust-supports the lower end of the main shaft 6 so as to be rotatable. A central plane portion of the upper frame 12 is an upper bearing portion 27 that rotatably supports the upper portion of the main shaft 6. The eccentric shaft portion 8 described above is located above the upper bearing portion 27 of the upper frame 12. The fixed scroll 2 and the orbiting scroll 3 described above have spiral teeth having substantially the same shape, and are combined so that the positions are 180 degrees out of phase with each other. The center of the fixed scroll 2 is on the axis C, and the center of the orbiting scroll 3 is in the eccentric position.

As shown in FIG. 2, an elongated hole 15 having a substantially rectangular shape in plan view is provided in the center of the plane of the slider 7. The long hole 15 is loaded with an eccentric shaft portion 8 having a substantially rectangular cross-sectional shape. An accommodation groove 16 is formed on a contact load surface 19 (an inner surface in the present invention) of the elongated hole 15 that receives a contact force (indicated by an arrow Fn in FIG. 2) from the eccentric shaft portion 8 when the main shaft 6 rotates. ing. A first slider plate 17 is accommodated in the accommodation groove 16. Further, in the scroll compressor 1, the second slider plate 18 is slidably interposed between the first slider plate 17 and the eccentric shaft portion 8.

The housing groove 16 is used for restricting the movement of the first slider plate 17 relative to the slider 7 in the slider sliding direction (arrow E direction: hereinafter abbreviated as the sliding direction). Therefore, in the state where the first slider plate 17 is housed in the housing groove portion 16, the gap between the first slider plate 17 and the housing groove portion 16 in the sliding direction needs to be sufficiently smaller than the sliding width of the slider 7. is there. The sliding width of the slider 7 is actually about 50 μm due to the sum of the shape tolerance and assembly tolerance of the fixed scroll 2 and the orbiting scroll 3, so that the distance between the first slider plate 17 and the receiving groove 16 in the sliding direction is The gap is preferably 20 μm or less. Further, the depth m in the contact load direction (arrow Fn direction) of the accommodation groove 16 is set to be equal to or less than the thickness of the first slider plate 17 so that the first slider plate 17 and the second slider plate 18 can slide. Yes. Therefore, the first slider plate 17 is positioned by the accommodation groove 16 in the sliding direction, and slides almost integrally with the slider 7. Further, the shape of the long hole 15 is a shape in which a sliding space 20 is secured so that the second slider plate 18 can sufficiently slide in the sliding direction of the slider 7.

And as shown in FIG. 3, the crowning shape part 14 is formed in the contact load surface of the eccentric shaft part 8 which contacts the 2nd slider plate 18. As shown in FIG. The crowning shape portion 14 is formed in a convex curve shape of an arc when viewed in a longitudinal section.

Next, the operation will be described.
In the scroll compressor configured as described above, when a power supply terminal (not shown) of the electric motor 23 is energized, torque is generated in the stator 4 and the rotor 5 and the main shaft 6 rotates. As a result, the orbiting scroll 3 supported by the slider 7 mounted on the eccentric shaft portion 8 of the main shaft 6 starts rotating. Then, the fluid gas is sucked from the suction pipe 10 and is sucked into the compression chamber 24 between the spiral teeth of the fixed scroll 2 and the spiral teeth of the orbiting scroll 3 in the compressor container 9 and then compressed. 11 and discharged outside the compressor container 9.

At that time, since the orbiting scroll 3 is restricted in rotation by an Oldham joint (not shown), the orbiting scroll 3 rotates only by revolution with a crank radius away from the axis C of the main shaft 6. At this time, centrifugal force accompanying the eccentric rotational motion of the orbiting scroll 3 acts on the eccentric shaft portion 8. Since the orbiting scroll 3 is made of a material such as aluminum or cast iron, when the main shaft 6 rotates at 7200 rpm, a centrifugal force of about 150 kgf is generated when an aluminum orbiting scroll is used. When an orbiting scroll is used, a centrifugal force of about 220 kgf is generated.

When the scroll compressor 1 is in operation, the radial force mainly consisting of the centrifugal force of the orbiting scroll 3 acts to increase the crank radius, and attempts to make the radial gap between the spiral teeth zero. Thereby, the inaccuracy of the shape of the spiral tooth is compensated, and the swinging scroll 3 can be rotated while being pressed against the fixed scroll 2, so that the leakage loss at the time of compression is reduced.

As described above, in the scroll compressor according to the first embodiment, the first slider plate 17 is fixed to the slider 7 with respect to the sliding direction by mounting the first slider plate 17 in the receiving groove portion 16, and the first slider plate 17 and the eccentric shaft are further fixed. Since the second slider plate 18 is slidably interposed between the two slider plates 17 and 18 and between the two slider plates 17 and 18 and the crowned shape portion 14 of the eccentric shaft portion 8 and the second slider plate 18. 2 Sliding occurs between the slider plate 18, and no sliding occurs between the slider 7 and the first slider plate 17. Therefore, wear on the inner surface of the long hole 15 of the slider 7 can be prevented. Sliding in the sliding direction is dispersed between the two slider plates 17 and 18 and between the crowning shape portion 14 of the eccentric shaft portion 8 and the second slider plate 18. However, since sliding mainly occurs between the two slider plates 17 and 18 having a small friction coefficient, it is possible to prevent wear of the crowning shape portion 14 of the eccentric shaft portion 8. As a result, even when the eccentric shaft portion 8 is deformed by the load received from the slider 7, the slider 7 and the bearing portion 28 of the orbiting scroll 3 can be kept parallel, and the scroll compressor 1 with high reliability is provided. can do.

Embodiment 2. FIG.
In the first embodiment, the tip surface 6A of the main shaft 6 is a flat surface, and the first slider plate 17 and the second slider plate 18 are supported on the flat surface. A second embodiment modified from the above will be described with reference to FIGS.
In the second embodiment, in addition to the configuration of the first embodiment, a groove portion 22 that is recessed in the direction of the axis C of the main shaft 6 is formed at the base position of the eccentric shaft portion 8 on the tip surface 6A of the main shaft 6. Since the groove portion 22 can be formed with a step from the base of the eccentric shaft portion 8 to the slider plate side, processing is easy. By shifting the position of this step from the base portion of the eccentric shaft portion 8 to both sides, the opposed inner wall portions 29 and 29 are formed. The lower end portion 18A (the end portion referred to in the present invention) of the second slider plate 18 is fitted into the groove portion 22 between the inner wall portions 29 and 29 so as to be mounted. Then, in a state where the second slider plate 18 is fitted in the groove portion 22, the side surface and the inner wall portion 29 of the second slider plate 18 in the sliding direction (the direction orthogonal to the paper surface of FIG. 4, that is, the direction of arrow E in FIG. 6). The width between the inner wall portions 29 and 29 is set so that the clearance between the inner wall portions 29 and 29 is sufficiently smaller than the sliding width of the slider 7.

The sliding width of the slider 7 is actually about 50 μm due to the shape tolerance of the fixed scroll 2 and the orbiting scroll 3, and therefore the gap between the second slider plate 18 and the inner wall portion 29 in the sliding direction is 20 μm or less. It is preferable. The depth k of the groove portion 22 is a depth at which the second slider plate 18 is fixed in the sliding direction, that is, a depth at which the second slider plate 18 on the groove portion 22 does not come out of the inner wall portions 29 and 29 during operation. Is set. Actually, since the corners of the first and second slider plates 17 and 18 are rounded, it is preferable to set the depth so that the rounded portions are completely fitted. In order not to move only the second slider plate 18 in the sliding direction, the width p of the inner wall portion 29 in the contact load direction (arrow Fn direction) is set so that both the first slider plate 17 and the second slider plate 18 are The width is set so as not to be fitted. As a result, the movement of the second slider plate 18 in the sliding direction is restricted by the inner wall portions 29, 29, so that the second slider plate 18 moves integrally with the eccentric shaft portion 8, while having a margin in the contact load direction.

As described above, the scroll compressor according to the second embodiment accommodates the lower end portion 18A of the second slider plate 18 and the groove portion 22 that restricts the movement of the second slider plate 18 in the sliding direction is the front end surface 6A of the main shaft 6. Therefore, the second slider plate 18 accommodated in the groove portion 22 is substantially fixed to the eccentric shaft portion 8 in the sliding direction. As a result, during the compressor operation, sliding occurs between the slider 7 and the first slider plate 17 and between the two slider plates 17 and 18, and the crowning shape portion 14 of the eccentric shaft portion 8 and the second slider No sliding occurs between the plates 18. Therefore, wear of the crowning shape portion 14 of the eccentric shaft portion 8 can be prevented. Further, since there is a spatial margin in the direction perpendicular to the sliding direction (arrow Fn direction), the second slider plate 18 can be inclined in the direction perpendicular to the sliding direction, and the function of crowning is maintained. it can. Then, the sliding in the sliding direction (arrow E direction) is distributed between the slider 7 and the first slider plate 17 and the sliding between the two slider plates 17 and 18. However, since sliding mainly occurs between the two slider plates 17 and 18 having a small friction coefficient, it is possible to prevent the inner surface of the long hole 15 of the slider 7 from being worn. In this case, since the friction coefficient between the second slider plate 18 and the crowning shape portion 14 of the eccentric shaft portion 8 is not related, the crowning shape portion 14 is not worn. Accordingly, the crowning function is maintained longer than in the first embodiment in which the first slider plate 17 is fixed to the slider 7 side. Incidentally, the wear on the inner surface of the long hole 15 of the slider 7 wears around the place most receiving the load from the crowning shape portion 14.

Embodiment 3 FIG.
In the first and second embodiments, the second slider plate 18 is illustrated in which the surface facing the eccentric shaft portion 8 is formed as a flat surface. However, the third embodiment in which the facing surface is modified is illustrated in FIGS. It is shown in FIG.
In the third embodiment, in addition to the configurations of the first and second embodiments, a concave surface 21 having a concave curved surface when viewed in a longitudinal section is formed on a surface of the second slider plate 18 facing the eccentric shaft portion 8. A part of the crowning shape portion 14 of the eccentric shaft portion 8 is accommodated in the recess 21. In this case, as shown in FIG. 8, the crowning shape portion 14 is formed so that the surface facing the recess 21 is substantially straight in the cross section. The second slider plate 18 is fixed to the eccentric shaft portion 8 in the sliding direction (the direction of arrow E) by fitting the crowns at both ends of the crowning shape portion 14 and the recess 21.

And as shown in FIG. 8, the recessed part 21 hardly forms the clearance gap of a sliding direction between the both sides | surfaces of the crowning shape part 14 of the eccentric shaft part 8. As shown in FIG. That is, the gap in the sliding direction is sufficiently smaller than the sliding width of the slider 7. The sliding width of the slider 7 is actually about 50 μm due to the sum of the shape tolerance and assembly tolerance of the fixed scroll 2 and the swing scroll 3. The gap between them is preferably 20 μm or less. Further, in order to maintain the function of the crowning shape portion 14, the concave portion 21 has a longitudinal section shape that is linear, or has a curvature R 1 that is larger than the curvature R of the longitudinal section shape of the crowning shape portion 14 and has a curvature R 1. Is formed in an arc shape with the same Z coordinate as the arc center of the crowning shape portion 14.

As described above, in the scroll compressor according to the third embodiment, the concave portion 21 is formed on the surface of the second slider plate 18 facing the eccentric shaft portion 8, so that a part of the crowning shape portion 14 is fitted into the concave portion 21. As a result, the second slider plate 18 moves substantially integrally with the eccentric shaft portion 8 in the sliding direction. Thereby, since sliding mainly occurs between the first slider plate 17 and the second slider plate 18, sliding between the second slider plate 18 and the crowning shape portion 14 can be suppressed, and the crowning shape portion 14. It is possible to reduce the wear of the steel.

In addition, when the longitudinal cross-sectional shape of the recessed part 21 is formed in circular arc shape like FIG. 7, the contact area which receives the load of the 2nd slider plate 18 and the crowning shape part 14 is large compared with the case where it forms in linear form. Therefore, the load per unit area becomes small. Thereby, the lifetime of the 2nd slider plate 18 and the crowning shape part 14 can be extended. That is, it is preferable to form the longitudinal cross-sectional shape of the recessed part 21 in the circular arc or the curve close | similar to a circular arc as mentioned above.

Embodiment 4 FIG.
In Embodiments 1 to 3, the surface roughness of the surface of each member was not mentioned, but the surface roughness of the surface of each member will be described in Embodiment 4 shown in FIG.
Here, the surface roughness of the contact load surface 19 of the long hole 15 of the slider 7 that receives the contact force from the eccentric shaft portion 8 is a, and the contact load surface 19 of the long hole 15 of the slider 7 is The surface roughness of the opposing surface is b, the surface roughness of the first slider plate 17 facing the second slider plate 18 is c, and the surface roughness of the second slider plate 18 facing the first slider plate 17 is c. The surface roughness of the surface of the second slider plate 18 facing the crowning shape portion 14 of the eccentric shaft portion 8 is e, and the surface roughness of the convex surface of the crowning shape portion 14 of the eccentric shaft portion 8 is d. Let f. Each surface roughness a, b, c, d, e, f is set so as to satisfy the following relational expressions (1) and (2).
a ≧ b> c (1), f ≧ e> d (2):

That is, the surface roughness c of the first slider plate 17 and the surface roughness d of the second slider plate 18 are set to be finer than the other surface roughnesses a, b, e, and f. Thereby, the space between the first slider plate 17 and the second slider plate 18 in the fluid lubrication state is increased between the slider 7 and the first slider plate 17 as the amount of the adsorbed film increases due to the substantial increase in the contact area. The friction coefficient is smaller than that between the crowning shape portion 14 and the second slider plate 18, and the wear amount is also reduced. Therefore, sliding mainly occurs between the first slider plate 17 and the second slider plate 18. As a result, sliding between the second slider plate 18 and the crowning shape portion 14 can be reduced.

Incidentally, since the surface roughness of the crowning shape portion 14 is about Rz1.5, the second slider plate 18 does not wear the crowning shape portion 14. In order to mainly slide between the first slider plate 17 and the second slider plate 18, the first and second slider plates satisfy the following relational expressions (3) and (4). It is more preferable to set the surface roughness b, c, d, e of 17 and 18.
c≈d ≦ Rz0.4 (3), e≈b≈Rz0.8 (4)

As described above, in the fourth embodiment, the surface roughness a, b, c, d, e, f of each surface is set so as to satisfy the relationship of a ≧ b> c, f ≧ e> d. Therefore, it is possible to improve the slidability between the first and second slider plates 17 and 18 in the fluid lubrication state, and the sliding mainly occurs between the first slider plate 17 and the second slider plate 18. Can be made. As a result, it is possible to reduce the wear of the crowning shape portion 14 of the eccentric shaft portion 8.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 2 Fixed scroll 3 Oscillating scroll 4 Stator 5 Rotor 6 Main shaft 6A Front end surface 6B Oil supply passage 7 Slider 8 Eccentric shaft portion 9 Compressor container 14 Crowning shape portion 15 Slot 16 Receiving groove portion 17 First slider plate 18 Second slider plate 18A Lower end (end)
19 Contact load surface (inner surface)
21 concave portion 22 groove portion 23 electric motor 24 compression chamber 29 inner wall portion C axis D eccentricity E arrows a to f surface roughness

Claims (4)

An electric motor, a main shaft connected to the electric motor to be driven to rotate, an eccentric shaft portion provided at a position deviated from an axis of the main shaft on a front end surface of the main shaft, and an elongated hole that accommodates the eccentric shaft portion. A first slider provided between the eccentric shaft portion and an inner surface of the elongated hole that receives contact force from the eccentric shaft portion when the main shaft rotates; A slider plate, an accommodation groove formed on the inner surface of the elongated hole and accommodating the first slider plate, a swing scroll pivotally supported by the slider and revolving around the axis of the main shaft, A scroll compressor that is fixed to a compressor container and forms a compression chamber with the orbiting scroll, wherein the fluid is sucked into and discharged from the compression chamber by the revolution of the orbiting scroll; 1st slider Scroll compressor being characterized in that interposed the second slider plate slidably between rate and the eccentric shaft portion. A groove portion recessed in the axial direction of the main shaft is formed at the root position of the eccentric shaft portion on the tip surface of the main shaft, and the groove portion is formed in the slider sliding direction between the second slider plate mounted on the groove portion and the groove portion. The scroll compressor according to claim 1, wherein the gap is configured to be smaller than a slider sliding width. 3. A concave portion for accommodating a crowning shape portion having a convexly curved cross section formed in the eccentric shaft portion is formed on a surface of the second slider plate facing the eccentric shaft portion. Scroll compressor described in 1. The surface roughness of the inner surface of the elongated hole that receives the contact force from the eccentric shaft portion by the slider is defined as a, and the surface roughness of the surface of the first slider plate that faces the inner surface of the elongated hole of the slider is defined as b. The surface roughness of the slider plate facing the second slider plate is c, the surface roughness of the second slider plate facing the first slider plate is d, and the second slider plate is the eccentric shaft. The surface roughness of the surface facing the crowning shape portion of the portion is e, and the surface roughness a, b, c, d, e, f is the surface roughness f of the surface of the crowning shape portion of the eccentric shaft portion. The following relational expressions (1) and (2):
a ≧ b> c (1), f ≧ e> d (2):
The scroll compressor according to any one of claims 1 to 3, wherein the scroll compressor is set so as to satisfy.

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