Scroll compressor

Abstract

A scroll compressor is disclosed. A plurality of grooves (85) communicating with each other are formed on a sliding surface of a thrust bearing (53) subjected to the axial force received by a movable scroll (32). The areas surrounded by the plurality of the grooves (85) make up a plurality of insular pressure receiving portions (83) independent of each other. The pressure receiving portions (83) represent at least one half of the area of the sliding surface.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a longitudinal sectional view showing a scroll compressor according to a first embodiment.

FIG. 2A is a diagram showing a movable-side sliding surface of the thrust bearing of the scroll compressor shown in FIG. 1.

FIG. 2B is a sectional view taken along line B-B in FIG. 2A in such a manner that the cross section of the substantially circular concavo-convex surface is visible.

FIG. 2C is an enlarged view of the portion designated by the reference character G in FIG. 2A.

FIG. 3 is a diagram showing the manner in which the oil film is formed on the insular pressure receiving portions on the movable-side sliding surface shown in FIG. 2 and the pressure thereof.

FIGS. 4A and 4B are diagrams showing the manner in which the oil film is formed in the case where a multiplicity of circular grooves are formed as oil pools on the sliding surface of the thrust bearing and the pressure thereof.

FIG. 5 is a diagram showing size of the area X of the grooves 85 of the four adjacent pressure receiving portions and the size of the area Y of the pressure receiving portion 83.

FIG. 6 is a diagram showing the manner in which the scroll-side plate 53a is moved in the cylindrical case 13a with the orbiting of the movable scroll 32.

FIG. 7 is a diagram showing the relation between the roughness of the bottom surface of the grooves 85 and the amount of oil attached with the lapse of time.

FIG. 8 is a diagram showing the sliding surface of the thrust bearing 53 comprised of the pressure-receiving unit 83 reduced in size progressively toward the inner peripheral side thereof.

FIG. 9 is a diagram showing the sliding surface of the thrust bearing 53 configured in such a manner that the groove 8 assume a hexagonal pattern.

FIG. 10 is a diagram showing the sliding surface of the thrust bearing 53 configured in such a manner that the pressure receiving portions 83 are arranged in tiles.

FIG. 11A is a diagram showing the area of a substantially circular flat portion having a tapered portion with curved corners in a polygonal island.

FIG. 11B is a sectional view taken along line A-A in FIG. 11A.

FIG. 11C is a sectional view taken along line B-B in FIG. 11A.

FIG. 12 is a longitudinal section view of a scroll compressor according to a second embodiment of the invention.

FIG. 13 is an enlarged sectional view showing the essential parts of the thrust bearing of FIG. 1.

FIGS. 14A and 14B are diagrams for explaining the effective radius of the pressure receiving portions.

FIG. 15 is a further enlarged view of a part of FIG. 13.

FIG. 16 is a diagram for explaining the relation between γ and W/R.

FIG. 17 is schematic diagram showing, in an enlarged form, the essential parts of the sliding surfaces of the thrust bearing.

FIG. 18 is a schematic diagram for explaining the method of evaluating the abrasion loss.

FIG. 19 is a longitudinal sectional view showing a scroll compressor according to a sixth embodiment of the invention.

FIG. 20 is a perspective view of the Oldham ring used with the scroll compressor described above.

FIG. 21 is a front view showing the sliding surface side of the movable scroll of the scroll compressor shown in FIG. 19.

FIG. 22 is a front view showing the sliding surface side of the movable scroll of the scroll compressor according to a seventh embodiment.

FIG. 23 is a front view showing the sliding surface side of the movable scroll of the scroll compressor according to an eighth embodiment.

FIG. 24 is a front view showing the sliding surface side of the movable scroll of the scroll compressor according to a ninth embodiment.

FIG. 25 is a front view showing the surface of the bearing member on the side in opposed relation to the movable scroll of the scroll compressor according to a tenth embodiment.

FIG. 26 is a front view showing the sliding surface side of the movable scroll of the conventional scroll compressor.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

First Embodiment

A first embodiment of the invention is described below with reference to FIGS. 1 to 7.

FIG. 1 is a longitudinal sectional view showing a scroll compressor 11 according to this embodiment. This embodiment represents a compressor for a water heater in the refrigeration circuit which uses carbon dioxide as a refrigerant and in which the pressure of carbon dioxide discharged exceeds the critical pressure thereof. Nevertheless, the invention is not limited to this compressor.

The scroll compressor 11 according to this embodiment is a motor driven hermetic compressor having a closed container 13 accommodating a motor unit 27 and a compression mechanism 10.

The closed container 13 includes a cylindrical case 13a, a motor-side end case 13b assembled and a compression mechanism-side end case 13c at each end of the cylindrical case 13a.

The motor unit 27 includes a stator 25 fixed on the inner peripheral surface of the cylindrical case 13a and a rotor 23 fixed on the shaft 21 rotationally driven by the motor unit 27.

The compression mechanism 10 includes a middle housing 15 fixed at a position adjacent to the stator 25 in the cylindrical case 13a, a movable scroll 32 orbited by a crank mechanism 28 supported by a main bearing 17 arranged on the middle housing 15, and a fixed scroll 38 fixed on the cylindrical case 13a on the side of the middle housing 15 far from the stator 25 in opposed relation to the movable scroll 32 thereby to form a working chamber 45 described later.

The shaft 21 is supported substantially horizontally by a main bearing 17 and an auxiliary bearing 19 fixed on a discal support member 14 interposed between the stator 25 and the motor-side end case 13b in the cylindrical case 13a.

The movable scroll 32 includes a substantially discal movable-side plate 33, a movable-side spiral 41 erected in an involute curve toward the fixed scroll 38 from the end surface of the movable-side plate 33 and a boss 35 erected cylindrically toward the middle housing 15 from the end surface far from the movable-side spiral 41.

The fixed scroll 38 includes a fixed-side plate 39 fixed on the cylindrical case 13a and a fixed-side spiral 43 formed of a spiral groove arranged on the end surface of the fixed-side plate 39 nearer to the movable scroll 32.

The middle housing 15 assumes the form of a triple-step cylinder having a progressively larger diameter toward the fixed scroll 38 from the motor unit 27. The cylinder 15a having the smallest diameter near to the motor unit 27 makes up a main bearing 17, and the middle cylinder 15b makes up a crank chamber 29 for accommodating the crank mechanism 28. The cylinder 15c having the largest diameter near to the fixed scroll 38, on the other hand, forms a scroll housing 31 for accommodating the movable scroll 32 and fixed on the inner peripheral surface of the cylindrical case 13a by a fixing means such as shrink fitting.

The crank mechanism 28 is comprised of an eccentric shaft 37 arranged integrally at the end of the shaft 21 nearer to the compression mechanism 10 and the boss 35 of the movable scroll 32. The eccentric shaft 37 is decentered a given amount e (FIG. 2A) from the axial center of the main bearing 17 and the auxiliary bearing 19. This eccentricity e makes up the orbital radius of the movable scroll 32.

An Oldham coupling not shown is arranged on the end surface (hereinafter referred to as the disk-unit scroll-side end surface 15e) of the disk unit 15d, nearer to the movable scroll 32, connecting the large-diameter cylinder 15c and the middle cylinder 15b making up the middle housing 15 thereby to prevent the rotation of the movable scroll 32. As a result, the movable scroll 32 is permitted only to orbit. In the compression mechanism 10, the volume of the working chamber 45 formed by mesh between the movable-side spiral 41 and the fixed-side spiral 43 is reduced by the revolution of the movable scroll 32 with respect to the fixed scroll 38 thereby to compress the refrigerant supplied to the intake chamber 46 communicating with the outermost peripheral side of the fixed-side spiral 43.

Also, a thrust bearing 53 is arranged between the disk-unit scroll-side end surface 15e and the end surface of the movable scroll 32 formed with the boss 35 (hereinafter referred to as the movable scroll back surface 32a). This thrust bearing 53 is a slide bearing for sliding between the movable scroll back surface 32a and the disk-unit scroll-side end surface 15e under the axial force (in this embodiment, the force pushing the movable-side plate 33 from the fixed scroll 38 toward the disk unit 15d) received by the movable-side plate 33 due to the difference between the reaction force generated at the time of compression of the refrigerant and the force generated in thrust direction by the pressure on the movable scroll back surface 32a. This thrust bearing 53 is explained in detail later.

The intake chamber 46 is arranged on the side surface of the fixed-side plate 39 and connected with an intake tube 47 for introducing the refrigerant from the refrigerant circuit external to the closed container 13 through the cylindrical case 13a.

A discharge port 49 is formed axially through the fixed-side plate 39 at the central portion of the fixed-side spiral 43. The refrigerant compressed by the movable scroll 32 and the fixed scroll 38 is discharged into a discharge chamber 50 from the discharge port 49.

The discharge chamber 50 is comprised of a depression formed by the end surface (hereinafter referred to as the fixed scroll back surface 38a) on the side of the fixed-side plate 39 far from the movable scroll 32 and the end surface of the separator block 55, nearer to the fixed-side plate 39, fixed on the fixed scroll back surface 38a. Incidentally, the discharge chamber 50 has therein a discharge valve 61 for preventing the reverse flow of the refrigerant discharged.

The high-temperature high-pressure refrigerant discharged into the discharge chamber 50 is led to an oil separator 63 through a refrigerant path 57 extending upward from the discharge chamber 50.

The oil separator 63 is of centrifugal double-cylinder type and includes an inner cylinder 63a and an outer cylinder 63b.

The refrigerant path 57, after extending upward along the fixed scroll back surface 38a from the discharge port 50, is connected, substantially tangentially, to the space between the inner cylinder 63a and the outer cylinder 63b of the centrifugal oil separator 63. The refrigerant flowing into the space between the inner cylinder 63a and the outer cylinder 63b substantially in tangential direction revolves in the space between the inner cylinder 63a and the outer cylinder 63b. After the oil contained in the refrigerant is centrifugally separated, the refrigerant is sent to the refrigerant circuit external to the closed container 13 through the inner cylinder 63a and the discharge tube 59. According to this embodiment, the oil preferably comprises, as a main component, a lubricating oil composed of selected one of polyalkylene glycol, polyvinyl ether and polyol ester or any combination thereof.

Incidentally, the outer cylinder 63b of the oil separator 63 is comprised of a cylindrical hole formed in the separator block 55, and the inner cylinder 63a is fixed by a fixing means such as press fitting or a circlip into the cylindrical hole making up the outer cylinder 63b.

Also, the discharge chamber 59 is hermetically inserted into the upper end of the cylindrical hole making up the outer cylinder 63b through the wall of the closed container 13. Incidentally, the space between the separator block 55 and the compression mechanism-side end case 13c constitutes an atmosphere lower in pressure than the refrigerant discharged.

The oil separated by the oil separator 63 moves downward by gravitation along the inner wall surface of the outer cylinder 63b, and stored in a high-pressure oil storage 65 through a small-diameter hole 64 formed at the lower end of the cylindrical hole of the outer cylinder 63b.

The high-pressure oil storage 65 is arranged in the separator block 55, and located under the cylindrical hole making up the outer cylinder 63b and the discharge chamber 50. In order to increase the amount of the high-pressure oil that can be stored in the high-pressure oil storage 65, the separator block 55 is configured so that the lower portion thereof making up the high-pressure oil storage 65 is projected toward the compression mechanism-side case 13c more than the upper portion thereof corresponding to the cylindrical hole making up the outer cylinder 63b.

The oil stored in the high-pressure oil storage 65 is led to the oil path 69 in the movable-side plate 33 by way of the oil return path 67 through the fixed-side plate 39 under the fixed-side spiral 43. Incidentally, a small-diameter restrictor 67a is arranged at the outlet of the oil return path 67.

The inlet of the oil path 69 opens to the surface of the movable-side plate 33 having the movable-side spiral 41. This inlet is countersunk to secure a larger sectional area than the other parts of the oil path 69. The inlet of the oil path 69 is adapted to communicate intermittently with the outlet of the oil return path 67 by the orbiting motion of the movable scroll 32. Also, the outlet of the oil path 69 is open to the inner wall of the boss 35 to communicate with the space between the end portion of the shaft 21 and the bottom surface of the boss 35.

Incidentally, the oil stored in the high-pressure oil storage 65, though high in pressure due to the discharge pressure of the refrigerant, is reduced to the desired pressure level by the intermittent communication between the oil return path 67 and the oil path 69 due to the orbiting motion of the movable scroll 32 and the restrictor 67a.

The oil led to the space between the end portion of the shaft 21 and the bottom surface of the boss 35 flows into the oil path 71 formed axially through the shaft 21.

The oil that has passed through the oil path 71 is led between the motor-side end case 13b and the support member 14 in the closed container 13. The support member 14, the middle housing 15 and the fixed-side plate 39 have a gap, not shown, with the cylindrical case 13a. The oil that has been led between the motor-side end case 13b and the support member 14, therefore, is stored over the entire inner lower part of the closed container 13. The entire inner lower part of the closed container 13 makes up a low-pressure oil storage 66.

The oil stored in the low-pressure oil storage 66 reaches the scroll housing 31 through the oil return hole 73 formed in the lower part of the disk unit 15d of the middle housing 15.

The oil path 71 has arranged therein diametrical holes 71a, 71b branching from the oil path 71 at the parts thereof corresponding to the main bearing 17 and the auxiliary bearing 19.

The outlet of the diametrical hole 71a communicates with the shaft groove 21a arranged on the shaft 21, and the oil that has flowed into the diametrical hole 71a, after lubricating the main bearing 17, the crank mechanism 28 and the thrust bearing 53, reaches the scroll housing 31. An oil groove 72 for establishing communication between the diametrical hole 71a and the thrust bearing 53 is formed on the middle cylinder 15b above the shaft 21 to lead the oil to the thrust bearing 53 above the shaft 21.

The oil that has flowed into the diametrical hole 71b, on the other hand, after lubricating the auxiliary bearing 19, drops into the low-pressure oil storage 66 and reaches the scroll housing 31 through the oil return hole 73.

The oil return path 67, the oil paths 69, 71 and the diametrical hole 71a make up an oil supply means for supplying the oil to the thrust bearing 53 due to the pressure difference between the oil separated by the oil separator 63 and the portion where the thrust bearing 53 is arranged.

The oil that has reached the scroll housing 31 is supplied to the sliding surfaces of the movable scroll 32 and the fixed scroll 38, compressed together with the refrigerant in the working chamber 45, and separated from the refrigerant by the oil separator 63.

Next, the thrust bearing 53 according to the invention will be explained. The thrust bearing 53 according to the invention is comprised of a scroll-side plate 53a fixed on the movable scroll back surface 32a and a housing-side plate 53b fixed on the disk-unit scroll-side end surface 15e.

The scroll-side plate 53a is formed in the shape of a donut, of which central hole is penetrated by the boss 35. The end surface of the scroll-side plate 53a in sliding contact with the housing-side plate 53b is formed with substantially circular concavo-convex portions as shown in FIG. 2A.

FIG. 2A is a sectional view taken along line A-A in FIG. 1 in such a manner that the end surface of the scroll-side plate 53a in sliding contact with the housing-side plate 53b is visible. FIG. 2B is a sectional view taken along line B-B in FIG. 2A in such a manner that the cross section of the substantially circular concavo-convex portions is visible, and FIG. 2C is an enlarged view of the portion designated by G in FIG. 2A. In FIG. 2A and FIG. 6 described later, the housing-side plate 53b indicated by dashed line and the radially inward edge 53c of the housing-side plate 53b, though invisible in the FIGS. 2A and 6, are shown in FIGS. 2A and 6 to indicate the relative positions thereof with the housing-side plate 53a.

The depressed parts of the substantially circular concavo-convex portions are comprised of a plurality of grooves 85. The plurality of the grooves 85, supplied with the oil by the oil supply means, are formed in a network pattern with intersections 85a having a larger groove width than the other parts. Also, the bottom surface roughness of each groove 85 shown in FIG. 2B is not less than 12.5 Rz and larger than the surface roughness of the pressure receiving portions 83 described later. Of all the plurality of the grooves 85, the groove 85b located on the outermost periphery (hereinafter referred to as the outermost peripheral groove 85b) makes a round in zigzag along the edge of the scroll-side plate 53a. Between the outermost peripheral groove 85b and the edge of the scroll-side plate 53a, an outer peripheral seal portion 81 is formed and kept in sliding contact with the housing-side plate 53b over the whole periphery thereby to reduce the amount of the lubricating oil flowing out from the sliding surfaces. The seal portion 81 has protrusions 81c curved to expand radially inward of the scroll-side plate 53a by the zigzag form of the outermost peripheral groove 85b. As shown in FIG. 2C, the protrusions 81c, like the pressure receiving portions 83 described later, have the function of forming an oil film by pulling in the oil from all the directions faced by the protrusions 81c due to the revolving motion of the movable scroll 32.

The protrusions surrounded by and formed between the plurality of the grooves 85 constitute the insular pressure receiving portions 83, which are formed substantially circular and arranged in staggered fashion conforming with the zigzag of the outermost peripheral grooves 85. For the purposes of exclusion of foreign matter and reducing the contact pressure, the diameter of the pressure receiving portions 83 is desirably not less than the orbital radius but less than twice the orbital radius, i.e. not less than e but less than 2e (e: amount of eccentricity of the movable scroll 32) on the one hand, and the area ratio of the pressure receiving portions 83 to the grooves 85 on the sliding surface of the scroll-side plate 53a is desirably not less than 50%. Also, the upper surface of the seal portion 81 and the pressure receiving portions 83 are smoothed as the sliding surface and substantially flush with each other. As shown in FIG. 2B, tapered portions or sagged roundish portions 81b, 83b are formed along the edge of the pressure receiving portions 83 to generate the wedge effect of the oil film, and the housing-side plate 53b is in sliding contact with the flat portions 81a, 83a.

Also, according to this embodiment, the thrust bearing 53 is formed with the concavo-convex portions on the scroll-side plate 53 fixed on the movable scroll 32, and therefore, the plurality of the grooves 85 making up the concavo-convex portions are moved relatively to the shaft 21 with the revolution of the movable scroll 32.

In the housing-side plate 53b, the surface in sliding contact with the scroll-side plate 53a is mirror-finished as a plane flat surface. The housing-side plate 53b thus assumes a donut-like form similar to the scroll-side plate 53a.

With this configuration, the oil held in the grooves 85 forms an oil film 86, as shown in FIG. 3, on the pressure receiving portions 83 due to the wedge effect of the sagged portions and the tapered portions 81b, 83b formed around the pressure receiving portions 83 by the sliding contact between the scroll-side plate 53a and the housing-side plate 53b. This oil film 86 contains the refrigerant dissolved therein.

According to this embodiment, the bottom surface of the grooves 85 has a large degree of roughness, and therefore, the lubricating oil can be positively held on the rough surface. As a result, even in the case where the scroll compressor 11 is operated with the oil supply temporarily suspended to the sliding surfaces of the thrust bearing 53, the sliding surfaces can be sufficiently lubricated by the oil held on the bottom surface of the grooves 85.

FIG. 7 is a diagram showing the relationship between the degree of roughness of the bottom surface of the grooves 85 and the amount of oil attached with the lapse of time. In FIG. 7, circles, squares, asterisks and crosses are symbols referring to test pieces having different degrees of roughness of the bottom surface of the grooves 85. In order to measure the amount of oil attached, the grooves 85 of test pieces are left in vertical positions and a predetermined amount of the oil equivalent to the refrigerator oil during the operation of the compressor is applied. Then, the weight of the oil with the lapse of time is measured. As a measure of the characteristic to be satisfied by the compressor used for the water heater, the operation pattern of the water heater is assumed as eight hours in operation followed by 16 hours out of operation, and the amount of the oil attached recognizable (one thirties) upon the lapse of 16 hours is used. Although in the case of the roughness of less than 12.5 z, no oil was detected, in the case of the roughness of 12.5 z it has been found that the deposition of the oil in measurable amount can be confirmed and the oil film can be held effectively.

Also, according to this embodiment, a plurality of the grooves 85 communicating with each other are formed on the sliding surface of the thrust bearing 53 to store the oil, and the amount of the oil flowing out of the sliding surfaces is reduced by the seal portion 81. Even in the case where the scroll compressor 11 is operated with the oil supply temporarily suspended to the sliding surfaces, therefore, the sliding surfaces can be sufficiently lubricated with the stored oil.

Also, according to this embodiment, the plurality of the grooves 85 are formed in a network pattern and communicate with each other, and therefore, the oil can be supplied between the grooves in communication with each other. Thus, the seizure is less likely to occur which otherwise might be caused by the short supply of the oil.

If the grooves formed on the sliding surface are independent of each other, the oil would fail to be refilled and a negative pressure would occur on the sliding surfaces in the case where the oil flows out of the sliding surfaces with the oil supply suspended. Then, the sliding surfaces would stick to each other and develop the seizure. According to this embodiment, however, the grooves 85 communicate with each other and therefore the negative pressure is prevented from being generated.

Also, in view of the fact that the plurality of the grooves 85 are formed in a network pattern and the pressure receiving portions 83 surrounded by the grooves 85 are each in the shape of an island and defined by the grooves over the entire periphery thereof, the oil film 86 can be formed by the wedge effect from all the directions by the revolving motion of the movable scroll 32. Further, the width of the intersections 85a of the plurality of the network grooves 85 is larger than that of the remaining portions, and therefore, the oil can sufficiently cover all the plurality of the grooves 85.

Also, the pressure receiving portions 83 are each in the shape of a substantially circular island, and therefore, the lubricating oil can be introduced into the pressure receiving portions 83 from all the directions. Further, the pressure receiving portions 83, being formed in staggered fashion, can be arranged with high density. Thus, the oil film-forming part per unit area can be increased and a heavy load can be supported.

Also, the lubricating oil can be supplied to the portion of the thrust bearing above the shaft 21 due to the pressure difference between the oil separated by the oil separator 63 and the portion where the thrust bearing is arranged. Therefore, the lubricating oil can be led to the thrust bearing positively even in the scroll compressor with the shaft 21 supported in substantially horizontal direction.

Also, in view of the fact that the grooves 85 are formed on the scroll-side plate 53a fixed on the movable scroll 32, the grooves 85 are moved relatively to the shaft 21 with the revolution of the movable scroll 32. As a result, the oil held on the bottom surface of the grooves 85 is easily supplied in spray to the sliding surfaces.

Also, as shown in FIG. 4A, in the case where the grooves 85 are circular and the distance is short between adjacent grooves 85, the oil film formed would cover adjacent grooves 85 and lose the pressure. To cope with this problem, as shown in FIG. 4B, a method may be conceived in which the distance D between the adjacent grooves 85 is increased. This configuration, however, will reduce the portion where the oil film is formed, resulting in a lower supporting pressure.

In the thrust bearing 53 according to this embodiment, in contrast, as shown in FIG. 3, the insular pressure receiving portions 83 are formed in spaced and isolated relationship to each other, and the grooves 85 are formed continuously around the insular pressure receiving portions 83 arranged in spaced relation to each other. The insular pressure receiving portions 83, therefore, can be sufficiently supplied with the lubricating oil over a wide range from the surrounding grooves 85. As a result, even in the case where the insular pressure receiving portions 83 are arranged in proximity to each other with high density, the lubricating oil can be refilled on the sliding surfaces. This increases the area where the oil film is formed per unit area, and a heavy load can be supported, thereby providing a thrust bearing high in lubricity.

Also, as shown in FIG. 5, a square area formed by connecting the centers of the four adjacent pressure receiving portions 83 is designed in such an area ratio that the area Y of the pressure receiving portions 83 is larger than the area X of the grooves 85, 85a. Specifically, the minimum groove width is designed in a value smaller than the size of the pressure receiving portions 83.

Also, since the grooves 85 which are formed on the sliding surface 53a on the side of the movable scroll 32 and which hold the lubricating oil also move, the lubricating oil can be supplied to the sliding surfaces more uniformly.

Next, the relative positions of the pressure receiving portions 83 arranged on the scroll-side plate 53a and the housing-side plate 53b with the orbiting motion of the movable scroll 32 are explained with reference to FIG. 6. FIG. 6 is a diagram showing the manner in which the scroll-side plate 53a moves in the cylindrical case 13a with the orbiting of the movable scroll 32. With the orbiting motion of the movable scroll 32, the scroll-side plate 53a moves to the positions (a), (b), (c) and (d) in that order. Let H be the envelope plotted by the inner peripheral edge 53c of the housing-side plate 53b by the relative motions of the scroll-side plate 53a and the housing-side plate 53b. The plurality of the pressure receiving portions 83 are arranged only on radially outside the envelope H on the scroll-side plate 53a. As a result, even in the case where the movable scroll 32 moves by orbiting, the pressure receiving portions 83 are not displaced out of the housing-side plate 53b, and a sufficient oil film is formed by the oil held in the plurality of the grooves 85.

Incidentally, the envelope H according to this invention constitutes a circle larger by the revolution radius of the movable scroll 32 than the inner peripheral edge 53c of the housing-side plate 53b.

Second Embodiment

Although the shaft 21 is arranged in a horizontal direction in the first embodiment described above, the invention is not limited to this configuration, and applicable also to a compressor having the shaft 21 arranged vertically as shown in FIG. 12. In FIG. 12, the component parts identical with those of the first embodiment are designated by the same reference numerals, respectively.

In FIG. 12, the lubricating oil and the refrigerant flowing in from the intake tube 47 lubricate the auxiliary bearing 19 while at the same time being led to the motor chamber with the motor unit 27 arranged therein inside the closed container 13 through the opening formed in the support member 14. The refrigerant and the oil led to the motor chamber lubricate the main bearing 17 and the crank mechanism 28 on the one hand and the oil is supplied to the thrust bearing 53 through the vertical hole formed in the middle housing 15 and led to the intake chamber 46 on the other hand.

According to the aforementioned embodiments, the closed container 13 is comprised of three cases including the cylindrical case 13a, the motor-side end case 13b and the compression mechanism-side end case 13c. Nevertheless, the invention is not limited to this configuration, and any two of the three cases may be configured as a single part.

Also, according to the aforementioned embodiments, the fixed scroll 38 is fixed on the cylindrical case 13a. Nevertheless, the fixed scroll 38 may alternatively be fixed on the compression mechanism-side end case 13c or the middle housing 15.

Further, the support member 14, though fixed on the cylindrical case 13a according to the aforementioned embodiments, may alternatively be fixed on the motor-side end case 13b.

According to the aforementioned embodiments, the fixed-side spiral 43 is formed by the spiral groove formed on the end surface of the fixed-side plate 39. Nevertheless, the invention is not limited to this configuration, and the fixed-side spiral 43 may be erected from the end surface of the fixed-side plate 39 toward the movable scroll 38.

Also, according to the aforementioned embodiments, the eccentric shaft 37 is formed integrally with the end portion of the shaft 21. The invention, however, is not limited to this configuration, and the eccentric shaft 37 may be arranged displaceably with respect to the end portion of the shaft 21.

Also, according to the embodiments described above, the movable scroll back surface 32a is placed in a low-pressure atmosphere. The invention, however, is not limited to this configuration, and the pressure of the discharged refrigerant may be made to act on the movable scroll back surface 32a thereby to press the movable-side plate 33 against the fixed scroll. In this case, the movable-side plate 33 is pressed against the fixed scroll 38 from the disk unit 15d side, and therefore, the thrust bearing 53 may be arranged between the movable-side plate 33 and the fixed-side plate 39.

Also, according to the aforementioned embodiments, the thrust bearing 53 is comprised of the scroll-side plate 53a fixed on the movable scroll back surface 32a and the housing-side plate 53b fixed on the disk-unit scroll-side end surface 15e. The invention, however, is not limited to this configuration, and the movable scroll 32 may be formed directly with a plurality of the grooves 85 and the pressure receiving portions 83 for direct sliding contact. As another alternative, the thrust bearing 53 may be comprised of a single plate having a plurality of grooves or three or more plates.

Also, according to the embodiments described above, the pressure receiving portions 83 are each formed substantially in a circle and arranged in staggered fashion. The invention, however, is not limited to this configuration, and the pressure receiving portions 83 may alternatively be arranged in the shape of a cocoon or linearly. As another alternative, the plurality of the grooves 85 may be comprised of grooves radially extending from the center of the scroll-side plate 53a and annular grooves concentric with the scroll-side plate 53a in the form perpendicular to the radially extending grooves, or a plurality of spirally arranged grooves.

Also, according to the aforementioned embodiments, the scroll-side plate 53a fixed on the movable scroll is formed with concavo-convex portions so that the plurality of the grooves 85 may move relative to the shaft 21 with the revolution of the movable scroll 32. The invention, however, is not limited to this configuration, and without fixing the scroll-side plate 53a on the movable scroll 32, the grooves 85 may be configured to move relatively to the shaft 1 as the result of revolution of the movable scroll 32.

Also, according to the aforementioned embodiments, the outer peripheral seal portion 81, the pressure receiving portions 83 and the grooves 85, though formed on the scroll-side plate 53a, may alternatively be formed on the fixed-side sliding surface 53b of the scroll accommodation depression 31.

Also, according to the aforementioned embodiments, the oil supply means is employed by which the oil is supplied to the thrust bearing 53 due to the pressure difference between the oil separated by the oil separator 63 and the portion where the thrust bearing 53 is arranged. The invention, however, is not limited to this configuration, and any configuration can be employed in which the oil is led to the thrust bearing 53 and the oil supply means is not required to utilize the pressure difference.

Also, according to the embodiments described above, the plurality of the pressure receiving portions 83 are arranged only on radially outside the envelope H plotted by the inner peripheral edge of the housing-side plate 53b by the relative motion between the scroll-side plate 53a and the housing-side plate 53b. In the case where the outer diameter of the housing-side plate 53b is small and the scroll-side plate 53a is liable to be displaced out of the edge of the housing-side plate 53b with the revolution of the movable scroll 32, however, the pressure receiving portions 83 may be arranged only on radially inside the envelope (a circle smaller by the revolution radius than the outer diameter of the housing-side plate 53b) plotted by the outer peripheral edge of the housing-side plate 53b.

Also, as shown in FIG. 8, the thrust bearing 53 may be comprised of the pressure receiving portions 83 progressively reduced in size toward the inner periphery. As a result, the pressure receiving portions 83 can be arranged with high density.

Also, the thrust bearing 53 may be comprised of the grooves 85 in a hexagonal pattern as shown in FIG. 9. As another alternative, as shown in FIG. 10, the pressure receiving portions 83 may be arranged in tiles. In this case, the width of the grooves 85 may be unified. Further, in the case where the pressure receiving portions 83 are each formed as a polygon, the lubricating oil can be introduced from each side of the polygon thereby to form an oil film. Incidentally, in FIGS. 8 to 10, the same component parts as those in the first embodiment are designated by the same reference numerals, respectively.

Also, at the end portion of the pressure receiving portion 83 shown in FIGS. 9 and 10, a minuscule round “sagged” taper may be formed to generate the oil film effectively. Then, many edges on the diagonal lines of the polygon are removed, and therefore, the flat portions 81a in sliding contact with the mating member and formed with an oil film assume a substantially circular form with round corners as hatched in FIG. 11A.

Incidentally, FIG. 11A is a diagram showing the rectangular insular pressure receiving portions 83 as viewed from above. FIG. 11B is a sectional view taken along line A-A in FIG. 11A, showing the area of the tapered portion displaced from the diagonal lines of the rectangular insular pressure receiving portions 83. FIG. 11C is a sectional view taken along line B-B in FIG. 11A, showing the area of the tapered portion on the diagonal lines of the rectangular insular pressure receiving portions 83. Also, the “sagged” round taper is formed specifically by barreling or wrapping.

Third Embodiment

Next, a third embodiment of the invention will be explained. The parts of the compressor not described below in the third embodiment are similar to the corresponding parts, respectively, of the compressor described in the first embodiment above.

According to this embodiment, the thrust bearing 53, as shown in FIG. 13, includes a pair of sliding surfaces 100 and 101. The first sliding surface 100 constitutes the surface of a scroll-side plate 53a in opposed relation to the housing-side plate 53b. The second sliding surface 101, on the other hand, constitutes the surface of the housing-side plate 53b in opposed relation to the scroll-side plate 53a.

As described above, the first sliding surface 100, as shown in FIG. 2A, is formed with a multiplicity of insular pressure receiving portions 83. In the second sliding surface 101, on the other hand, the portion thereof in opposed relation to the first sliding surface 100 is substantially flat, as shown in FIG. 13. According to this embodiment, the second sliding surface 101 is planar and flat in its entirety.

In this specification, the wording “substantially flat” means that the portion of the second sliding surface 101 opposed to the pressure receiving portions 83 is flat between the pressure receiving portions 83 and the particular portion to such a degree as to generate the pressure due to the wedge effect in the mixed fluid of the lubricating oil and the refrigerant interposed between the pressure receiving portions 83 and the particular portion.

As shown in FIG. 13, the surface of each pressure receiving portion 83 nearer to the second sliding surface 101 has a sagged portion 83b formed along the peripheral edge thereof and a flat portion 83a connected with the sagged portion 83b inside the latter. The sagged portion 83b is arranged along the peripheral edge of the pressure receiving portion 83 by way of which the mixed fluid flows in. According to this embodiment, the revolving motion of the movable scroll 32 acts to introduce the mixed fluid from the entire peripheral edge of each pressure receiving portion 83, and therefore, the sagged portion 83b is formed over the entire peripheral edge of the pressure receiving portion 83.

According to this embodiment, the pressure receiving portions 83 are substantially circular, and so are the flat portions 83a. The flat portions 83a and the second sliding surface 101 are opposed to each other substantially in parallel to each other.

The sagged portion 83b is located between the outer peripheral edge of the pressure receiving portion 83 and the flat portion 83a. The outer peripheral edge of the sagged portion 83b is coincident with the outer peripheral edge of the pressure receiving portion 83, while the inner peripheral edge of the sagged portion 83b is coincident with the outer peripheral edge of the flat portion 83a. In other words, each sagged portion 83b is sandwiched between large and small concentric circles of different sizes.

Each sagged portion 83b is formed in a taper. As shown in FIG. 13, the interval between the sagged portion 83b and the second sliding surface 101 monotonically increases from inside toward outside of the pressure receiving portion 83.

As shown in FIG. 13, according to this embodiment, the outer peripheral edge of the pressure receiving portion 83 rises substantially vertically from the grooves 85. Incidentally, the sagged portion 83b may be extended outward of the pressure receiving portion 83 and connected with the groove 85 as shown by dotted lines in FIG. 13.

The groove 85 shown in FIG. 13 may be replaced by other grooves 85a, 85b.

The effective radius R of the pressure receiving portion 83 with respect to the amount of eccentricity (orbital radius) e of the movable scroll 32 is desirably designed appropriately in accordance with specific applications of the scroll compressor 11. Especially, from the viewpoint of exclusion of foreign matter and reduction in contact pressure, the ratio R/e between the effective radius R and the eccentricity e desirably satisfies the relation 0.4≦R/e≦1.0. From a similar viewpoint, the area ratio of the pressure receiving portions 83 to the grooves 85 on the first sliding surface 100 is desirably not less than 50%.

The effective radius R of the pressure receiving portion 83 is an indicator of the size of the portion of the pressure receiving portion 83 inward of the contour formed by the outer peripheral edge of the width W of the sagged portion 83b. The width W of the sagged portion 83b (FIG. 13) represents the length between the position of the sagged portion 83b where the height difference with the flat portion 83a of the first sliding surface 100 is 1 μm and the inner peripheral edge of the sagged portion 83b, as measured along the imaginary line passing through the center of the flat portion 83a.

According to this embodiment, the outer peripheral edge of the width W of the sagged portion 83b is coincident with the outer peripheral edge of the pressure receiving portion 83. Each pressure receiving portion 83 is substantially circular, and has the outer peripheral edge thereof coincident with that of the width W of the sagged portion 83b. Specifically, according to this embodiment, the plan view of the portion inside the contour formed by the outer peripheral edge of the width W of the sagged portion 83b is circular, and the effective radius R of the pressure receiving portion 83 is equal to the radius of the pressure receiving portion 83.

According to this embodiment, the pressure receiving portion 83 is circular. In the case where the pressure receiving portion 83 is oblong, elliptic or polygonal, however, as shown in FIG. 14A, the average value of the long diameter d1 and the short diameter d2 of the shape formed by the outer peripheral edge of the width W of the sagged portion 83b is regarded as the effective radius R. As an alternative, as shown in FIG. 14B, the equivalent radius of the circle having the same area S as the particular shape is regarded as the effective radius R. Specifically, the effective radius R is regarded as the equivalent radius of the circle having the same area S as the portion of the pressure receiving portion 83 inside the position of the sagged portion 83b where the difference of height with the flat portion 83a of the first sliding surface 100 is 1 μm.

FIG. 13 shows an example in which the width W is equal to the length between the outer and inner peripheral edges of the sagged portion 83b. Specifically, in this example, the difference of height between the outer peripheral edge of the sagged portion 83b and the flat portion 83a is 1 μm.

With regard to the height of the pressure receiving portion 83, the length between the flat portion 83a and the groove 85 as measured in the direction perpendicular to the flat portion 83a is desirably 0.1 to 0.5 mm to effectively generate the oil film on the one hand and to secure the exclusion of foreign matter and the load resistance of the pressure receiving portion 83 on the other hand. According to this embodiment, the grooves 85, 85a, 85b are formed to the same height.

From a similar point of view, the difference of height between the flat portion 83a and the outer peripheral edge of the sagged portion 83b is desirably such that the length measured in the direction perpendicular to the flat portion 83a is 0.5 to 5 μm.

The interval between the pressure receiving portions 83 is preferably 200 to 500% in terms of the percentage that the length between the centers thereof represents of the effective radius R in the circumferential direction of the scroll-side plate 53a. Also in the radial direction of the scroll-side plate 53a, 200 to 500% is preferable.

The thrust bearing 53 having the first and second sliding surfaces 100 and 101 assumes the state lubricated with the fluid under predetermined operating conditions due to the wedge effect of the pressure receiving portions 83.

Next, the state in which the thrust bearing 53 in the state lubricated with the fluid is further explained.

In the state where the thrust bearing 53 is lubricated with the fluid (hereinafter referred to as the state of hydrodynamic lubrication), the continuous oil film (not shown) due to the mixed fluid is formed between the first and second sliding surfaces 100 and 101. As shown in FIG. 13, therefore, the first and second sliding surfaces 100 and 101 are separated from each other by the oil film. In other words, the sliding surfaces 100 and 101 are out of contact with each other.

In FIG. 13, the minimum oil film thickness hmin is given as the thickness of the portion where the length between the pressure receiving portions 83 and the second sliding surface 101 is shortest. Specifically, the portion where the oil film thickness is minimum, is the flat portion 83a.

Also, in FIG. 13, the inlet oil film thickness hin is given as the height of the sagged portion 83b at the inlet where the mixed fluid flows in between the pressure receiving portions 83 and the second sliding surface 101. The oil film pressure begins to generate effectively from this inlet. In FIG. 13, the inlet oil film thickness hin is the length between the outer peripheral edge of the sagged portion 83b and the flat portion 83a of the first sliding surface 100.

Normally, the inlet oil film thickness hin is variable in the range of 0.1 to 4.0 μm depending on the operating conditions of the scroll compressor 11. Under typical operating conditions, hin is 1.0 μm.

FIG. 15 shows the manner, in enlarged form, in which the flat portion 83a of the pressure receiving portion 83 is in opposed relation to the second sliding surface 101. The first sliding surface 100 and the second sliding surface 101 have a surface roughness, respectively, and the thickness of the oil film existing between the sliding surfaces 100 and 101 changes with the surface roughness of the sliding surfaces 100 and 101.

With the increase in surface roughness of the sliding surfaces 100 and 101, the surface roughness transcends the thickness of the oil film capable of being formed, and the sliding surfaces are liable to contact each other.

From this viewpoint, the standard deviation σ1 of the surface roughness of the flat portion 83a of the first sliding surface 100 and the standard deviation σ2 of the surface roughness of the second sliding surface 101 are required to be not more than 0.08 μm, respectively.

In the case where the initial standard deviations σ1 and σ2 of the surface roughness of the sliding surfaces 100 and 101 are larger than 0.08 μm, the standard deviations σ1 and σ2 are reduced to not more than 0.08μ or preferably to not more than 0.04 μm by running-in before using the scroll compressor 11. Normally, the lower limit of the standard deviations σ1 and σ2 of the surface roughness after running-in is about 0.015 μm. At least after running-in, therefore, the standard deviations σ1 and σ2 are desirably 0.015 to 0.04 μm.

The composite surface roughness σc specified by Equation (2) below based on the standard deviations σ1 and σ2 below is used as an indicator of the surface roughness of the sliding surfaces 100 and 101.

σc=√{square root over (σ1²+σ2²)}  (2)

As long as the thrust bearing 53 is in the state of hydrodynamic lubrication, a continuous oil film exists between the flat portion 83a and the portion of the second sliding surface 101 in opposed relation to the flat portion 83a. For this purpose, the oil film parameter Λ for the sliding surfaces 100 and 101 specified by Equation (3) below satisfies the relation Λ≧3.

$\begin{array}{cc}\Lambda =\frac{h\min }{\sqrt{\sigma 1^2+\sigma 2^2}}=\frac{1}{\sqrt{\sigma 1^2+\sigma 2^2}}\gamma {{{R\left[\frac{\mathrm{hin}}{R}\right]}^{\alpha }\left[\frac{\eta ·\omega }{\mathrm{Pave}}\right]}^{\beta }\left[\frac{e}{R}\right]}^{\beta }& \left(3\right)\end{array}$

Equation (3) is determined from the lubricated state of the pressure receiving portions 83 of the sliding surfaces 100 and 101 and what is called an elastohydrodynamic lubricaton (EHL) theory. Incidentally, Equations (1) and (3) are identical with each other in substance.

The oil film parameter Λ, as shown in Equation (3), is the ratio of the minimum oil film thickness hmin to the composite surface roughness σc.

In the case where the oil film parameter Λ satisfies the relation Λ≧3, the minimum oil film thickness hmin is sufficiently larger than the composite surface roughness. Between the pressure receiving portions 83 and the second sliding surface 101, therefore, the continuous oil film always exists and the sliding surfaces 100 and 101 are separated from each other. Specifically, the state of hydrodynamic lubrication is established for the thrust bearing 53. This oil film is the EHL oil film or the fluid lubrication oil film.

In the case where the oil film parameter Λ satisfies the relation Λ<1, on the other hand, the pressure receiving portions 83 and the second sliding surface 101 are kept in contact with each other at a given point, and the sliding surfaces are in what is called a state of boundary lubrication. In the case where the oil film parameter Λ satisfies the relation 1≦Λ<3, on the other hand, the sliding surfaces are either in the partial EHL state or a state of mixed lubrication.

Equation (3) is further described below.

In Equation (3), η is the kinematic viscosity on the sliding surfaces 100 and 101 of the thrust bearing 53 under the operating conditions of the mixed fluid.

The center of the movable scroll 32 is decentered a given amount e from the axial center of the rotary shaft 21, and ω is the value obtained by dividing the sliding speed of the pressure receiving portions 83 with respect to the second sliding surface 101 by the eccentricity e. The eccentricity e, which is the orbital radius of the movable scroll 32, is normally 2.5 to 5 mm.

The characters Pave designates the average contact pressure of the pressure receiving portions 83.

The characters α and β designate constants calculated by the elastohydrodynamic lubricaton theory based on the lubrication conditions, and assuming that the inlet oil film thickness hin is 1 μm as shown in FIG. 13, α is about −0.4 while β is about 0.7.

Also, γ is the function of the width W and the effective radius R, and has the relation shown in FIG. 16 with the ratio W/R between the width W of the sagged portion 83b and the effective radius R. The value γ increases with W/R and decreases after reaching the peak as shown in FIG. 16.

From Equation (3), the oil film parameter Λ is proportional to γ. Specifically, the oil film parameter Λ increases with γ. This value γ, as shown in FIG. 16, is the function of W/R. Therefore, the thrust bearing 53 is desirably designed in such a manner that W/R assumes a value associated with the substantially peak value of γ.

Also, from Equation (3), the oil film parameter Λ is the function of the ratio R/e between the effective radius R of the pressure receiving portions 83 and the eccentricity e. The ratio R/e is a value appropriately determined according to specific applications of the scroll compressor 11.

With R/e as a parameter, therefore, a desirable range of W/R exists in which the oil film parameter Λ satisfies the relation Λ≧3. The desirable range of W/R for the case in which the inlet oil film thickness hin shown in FIG. 13 is 1 μm is explained below.

In the case where the ratio R/e between the effective radius R and the eccentricity e is about unity, for example, the ratio between the width W of the sagged portion 83b and the effective radius R desirably satisfies the relation 0.05≦W/R≦0.98. In this case, the fact that R/e is about unity means that R/e is in the range of 0.8<R/e≦1.0.

Also, in the case where the ratio R/e between the effective radius R and the eccentricity e is about 0.8, the ratio between the effective radius R and the width W of the sagged portion 83b desirably satisfies the relation 0.1≦W/R≦0.85. In this case, the fact that R/e is about 0.8 means that R/e is in the range of 0.6<R/e≦0.8.

Further, in the case where the ratio R/e between the effective radius R and the eccentricity e is about 0.5, the ratio between the effective radius R and the width W of the sagged portion 83b desirably satisfies the relation 0.2≦W/R≦0.6. In this case, the fact that R/e is about 0.5 means that R/e is in the range of 0.4<R/e≦0.6.

These facts indicate that the oil film parameter Λ satisfies the relation Λ≧3, and therefore, the state of hydrodynamic lubrication is established for the thrust bearing 53. FIG. 16 shows the range of W/R in which the oil film parameter Λ satisfies the relation Λ≧3. In each value of R/e, the oil film parameter Λ fails to satisfy the relation Λ≧3 in the area where W/R is large and small. This is due to the reason described below.

With the decrease in the width W of the sagged portion 83b and the resulting decrease in W/R, the wedge effect is reduced and so is the minimum oil film thickness hmin, which in turn reduces the oil film parameter Λ. With the increase in the width W of the sagged portion 83b and the resulting increase in W/R, on the other hand, the flat portion 83a is reduced and therefore the oil film pressure generated is liable to be lost. This reduces the minimum oil film thickness hmin, thereby reducing the oil film parameter Λ.

Also, like in the pressure receiving portions 83, the state of hydrodynamic lubrication is desirably established between the seal portion 81 and the second sliding surface 101.

The state of hydrodynamic lubrication of the thrust bearing 53 is further explained below.

As described above, in order to positively secure the state of hydrodynamic lubrication of the thrust bearing 53, according to this embodiment, the scroll compressor 11 is operated preferably in such a manner that the mixed fluid containing the lubricating oil and the refrigerant is supplied to the sliding surfaces 100 and 101 of the slide bearing 53, the sliding speed of the pressure receiving portions 83 with respect to the second sliding surface 101 is set to not less than 0.5 m/sec, and the mixed fluid is interposed between the pressure receiving portions 83 and the second sliding surface 101. Thus, preferably, the load with the average contact pressure Pave of 0.5 to 20 MPa is exerted on the pressure receiving portions 83, and the kinematic viscosity of the mixed fluid under the operating conditions is maintained at 0.1 to 10 cst. The lubricating oil is desirably contained in the oil described above.

The operating conditions of this scroll compressor 11 are further explained. In the scroll compressor 11 according to this embodiment, the mixed fluid is supplied to the sliding surfaces 100 and 101 of the thrust bearing 53 by the oil supply means.

Also, as the result of orbiting of the movable scroll 32, the first sliding surface 100 fixed on the movable scroll 32 slides with respect to the second sliding surface 101 fixed on the middle housing 15. This sliding speed with respect to the second sliding surface 101 is preferably not less than 0.5 m/sec, or more preferably 0.6 to 5 m/sec.

Also, the load is imposed toward the second sliding surface 101 on the pressure receiving portions 83 of the thrust bearing 53 due to the difference between the reaction force of the compressed refrigerant and the force in the direction of thrust under the pressure from the movable scroll back surface 32a. The average contact pressure of the pressure receiving portions 83 due to this load is preferably 0.5 to 20 MPa, or more preferably, 2 to 15 MPa.

Further, the mixed fluid preferably has the kinematic viscosity of 0.1 to 10 cst, or more preferably, 4 to 10 cst on the sliding surfaces 100 and 101 of the thrust bearing 53 under the aforementioned operating conditions of the scroll compressor 11, where 1 cst is equal to about 1×10⁻⁶ m²/sec.

According to this embodiment, the scroll compressor 11 is used under the aforementioned operating conditions, so that an oil film is formed between the pressure receiving portions 83 and the portion of the second sliding surface 101 in opposed relation to the pressure receiving portions 83. Then, the pressure is generated in the oil film and supports the load generated on the sliding surfaces, thereby making it possible to use the thrust bearing 53 in the state of hydrodynamic lubrication. As a result, the wear of the thrust bearing 53 is prevented, and the scroll compressor 11 can be used while maintaining the performance thereof for a long time.

With the scroll compressor 11 according to this embodiment, the thrust bearing 53 has the continuous oil film formed between the pressure receiving portions 83 and the second sliding surface 101 in opposed relation to the pressure receiving portions 83, and therefore, can be used in the state of hydrodynamic lubrication. This scroll compressor is not complicated in the control operation and not high in cost.

Also, according to this embodiment, the ratio R/e between the effective radius R of the pressure receiving portions 83 and the orbital radius e of the movable scroll 32 is designed in accordance with a specific application on the one hand, and the ratio between the width W and the effective radius R is set in a predetermined range on the other hand thereby to positively establish the state of hydrodynamic lubrication of the thrust bearing 53.

Also, according to this embodiment, the roughness of the bottom surface of the grooves 85 is so large that the lubricating oil can be positively held on this rough surface. As a result, even in the case where the scroll compressor 11 is operated with the oil supply suspended temporarily to the sliding surfaces of the thrust bearing 53, the sliding surfaces can be sufficiently lubricated by the oil held on the bottom surface of the grooves 85.

Also, the plurality of the grooves 85 are formed in a network pattern, and the pressure receiving portions 83 each surrounded by the grooves 85 assume the shape of an island. Each of the pressure receiving portions 83, therefore, is surrounded by the grooves over the entire periphery thereof, with the result that the oil film 86 can be formed by the wedge effect from all the directions with the revolving motion of the movable scroll 32. Further, the groove width at the intersections 85a of the plurality of the network grooves is larger than that of the other portions, and therefore, the oil can be supplied sufficiently to the plurality of the grooves 85.

Also, the pressure receiving portions 83, which are each in the shape of a substantially circular island and formed in staggered fashion, can be arranged with a high density. Thus, the size of the oil film forming portion per unit area is increased and a heavy load can be supported.

Also, the grooves 85 are formed on the scroll-side plate 53a fixed on the movable scroll 32, and therefore, move relative to the shaft 21 with the revolution of the movable scroll 32. As a result, the oil held on the bottom surface of the grooves 85 is easily supplied to the sliding surfaces as a spray.

Next, with reference to FIG. 6, an explanation is given about the relative positions of the pressure receiving portions 83 arranged on the scroll-side plate 53a and the housing-side plate 53b with the orbiting of the movable scroll 32. FIG. 6 is a diagram showing the manner in which the scroll-side plate 53a moves in the cylindrical case 13a with the orbiting of the movable scroll 32. With the orbiting of the movable scroll 32, the scroll-side plate 53a moves to the positions (a), (b), (c) and (d) in that order. Let H be the envelope plotted by the inner peripheral edge 53c of the housing-side plate 53b due to the relative motion of the scroll-side plate 53a and the housing-side plate 53b. The plurality of the pressure receiving portions 83 are arranged only on radially outside the envelope H on the scroll-side plate 53a. As a result, even in the case where the movable scroll 32 is moved by orbiting, the pressure receiving portions 83 are not displaced out of the housing-side plate 53b, and a sufficient oil film is formed by the oil held in the plurality of the grooves 85.

According to this embodiment, the envelope H constitutes a circle larger by the revolving radius of the movable scroll 32 than the inner peripheral edge 53c of the housing-side plate 53b.

The preferred embodiments of the invention are explained above, and this invention is not limited to these embodiments.

Each pressure receiving portion 83, though circular according to this invention, may alternatively be, for example, oblong, elliptic, triangular, rectangular or otherwise polygonal.

Also, according to this embodiment, the sagged portion 83b is formed over the entire peripheral edge of the pressure receiving portions 83. Nevertheless, the sagged portion 83b may be formed only along the peripheral edge where the mixed fluid flows in. Also, the sagged portion 83b, though formed in a taper in this embodiment, may alternatively be formed in a curve.

According to this embodiment, the pressure receiving portions 83 are arranged in staggered fashion. Nevertheless, the invention is not limited to this configuration, and the pressure receiving portions 83 may alternatively be arranged in a regular grid, an oblique grid or at random.

Also, according to this embodiment, the outer peripheral seal portion 81, the pressure receiving portions 83 and the grooves 85 are formed on the scroll-side plate 53a. Nevertheless, the invention is not limited to this configuration, and they may be formed on the fixed-side sliding surface 53b of the scroll accommodation depression 31. In other words, the second sliding surface 101 may be fixed on the movable scroll 32.

According to this embodiment, the oil supply means is employed whereby the oil is supplied to the thrust bearing 53 due to the difference between the pressure of the oil separated by the oil separator 63 and the pressure of the portion where the thrust bearing 53 is arranged. Nevertheless, the invention is not limited to this configuration, and any configuration may be employed in which the oil is led to the thrust bearing 53 without using the pressure difference.

The operational effects of the scroll compressor according to the invention are further explained below.

The scroll compressor 11 shown in FIG. 1 is fabricated and the wear resistance of the thrust bearing 53 evaluated. The following evaluation conditions are used.

The standard deviations σ1 and σ2 of the surface roughness of the first and second sliding surfaces 100 and 101 are about 0.02 μm. The effective radius of the pressure receiving portions 83 is about 2.25 mm. The inlet oil film thickness hin is 1 μm. The kinematic viscosity of the mixed fluid under the operating conditions is 4 to 8 cst. The value obtained by dividing sliding speed of the pressure receiving portions 83 by the amount of eccentricity c is 260 to 314 1/sec. The average contact pressure Pave of the pressure receiving portions 83 is 6 to 10 MPa. The width W of the sagged portions 83b is about 1 mm. The eccentricity e is 2.5 mm. The oil film parameter Λ is 4 to 6.

The result of the wear resistance evaluation shows that the sliding surfaces 100 and 101 of the thrust bearing 53 are not worn even after movement for 3700 hours. This indicates that the state of hydrodynamic lubrication of the sliding surfaces 100 and 101 is maintained during the period of the wear resistance evaluation.

Fourth Embodiment

Next, a fourth embodiment of the invention will be explained. Incidentally, the parts of the compressor not described below in the fourth embodiment are similar to the corresponding parts, respectively, of the compressor described in the first embodiment.

According to the fourth embodiment, the thrust bearing 53 has a pair of sliding surfaces 100 and 101, as shown in FIG. 17. The first sliding surface 100 constitutes the surface of the scroll-side plate 53a in opposed relation to the housing-side plate 53b. The second sliding surface 101 makes up the surface of the housing-side plate 53b in opposed relation to the scroll-side plate 53a.

As described above, the first sliding surface 100 is formed with a multiplicity of insular pressure receiving portions 83. Also, the portion of the second sliding surface 101 in opposed relation to the pressure receiving portions 83 of the first sliding surface 100 is substantially flat as shown in FIG. 17. According to this embodiment, the second sliding surface 101 is a planar flat surface in its entirety.

The grooves 85 shown in FIG. 17 may be replaced by the grooves 85a, 85b.

As shown in FIG. 17, the surface of each pressure receiving portion 83 nearer to the second sliding surface 101 has a sagged portion 83b formed along the peripheral edge thereof and a flat portion 83a connected to the sagged portion 83b. The sagged portion 83b is arranged on the peripheral edge of the pressure receiving portion 83 where the mixed fluid flows in. According to this embodiment, the mixed fluid is introduced from the entire peripheral edge of the pressure receiving portion 83 with the revolving motion of the movable scroll 32, and therefore, the sagged portion 83b is formed over the entire peripheral edge of the pressure receiving portion 83.

On the first and second sliding surfaces 100 and 101, the state of hydrodynamic lubrication is easily established by the wedge effect of the pressure receiving portions 83. At the time of starting the scroll compressor 11 or liquid back, however, the boundary or mixed lubrication may occur.

The “liquid back” is a phenomenon in which a liquid-phase refrigerant is introduced into the scroll compressor 11 together with a gas-phase refrigerant from the intake tube 47, and the particular liquid-phase refrigerant flows in to the sliding surfaces 100 and 101. The liquid-phase refrigerant dilutes the lubricating oil on the sliding surfaces 100 and 101, and therefore, the boundary or the mixed lubrication is liable to occur on the sliding surfaces.

The first sliding surface 100 and the second sliding surface 101 each have a surface roughness, and the thickness of the oil film existing between the sliding surfaces 100 and 101 changes with the surface roughness of the two sliding surfaces 100 and 101.

The surface roughness of the sliding surfaces 100 and 101, if large, overcomes the thickness of the oil film to be formed, and the sliding surfaces easily come into contact with each other.

From this viewpoint, the standard deviation σ1 of the surface roughness on the flat portion 83a of the first sliding surface 100 and the standard deviation σ2 of the surface roughness on the second sliding surface 101 are preferably not larger than 0.08 μm.

In the case where the standard deviations σ1 and σ2 of the initial surface roughness of the sliding surfaces 100 and 101 is larger than 0.08 μm, the standard deviations σ1 and σ2 of the surface roughness are desirably reduced to not more than 0.08 μm or preferably to not more than 0.04 μm by running-in before using the scroll compressor 11. Normally, the lower limit of the standard deviations σ1 and σ2 of the surface roughness after the running-in is about 0.015 μm. At least after the running-in, therefore, the standard deviations σ1 and σ2 are preferably 0.015 to 0.04 μm.

The pressure receiving portions 83 preferably have the aforementioned relation between the diameter thereof and the orbital radius e. Also, the length of the sagged portion 83b of the pressure receiving portions 83 as measured along the imaginary line passing through the center of the flat portion 83a is preferably 5 to 98% of the radius of the pressure receiving portion 83, or more preferably, 30 to 50% to effectively secure the wedge effect on the mixed fluid.

The intervals between the pressure receiving portions 83 in terms of the length of the line between the centers thereof is preferably 200 to 500% of the diameter of the pressure receiving portion 83 along the circumferential direction of the scroll-side plate 53a. Similarly, it is preferably 200 to 500% along the radial direction of the scroll-side plate 53a.

The first sliding surface 100 and the second sliding surface 101 of the thrust bearing 53 are each formed of a steel material. In other words, the scroll-side plate 53a and the housing-side plate 53b are each formed of a steel material.

Examples of the steel material making up the sliding surfaces 100 and 101 preferably include a high-carbon chromium bearing steel, alloy steel for machine construction, cold-rolled steel plate, nickel-chromium steel, nickel-chromium-molybdenum steel, chromium steel, chromium-molybdenum steel, manganese steel for machine construction, manganese chromium steel and other various steel materials specified by JIS such as the steel with a guaranteed hardenability for machine construction.

More specifically, the high-carbon chromium bearing steel is preferably conforming with SUJ2, SUJ3 or SUJ4. Also, the carbon steel for machine construction is preferably SCr415, SCr420, SCr440, SCM415, SCM420, SNCM420, SCM435, SCM440 or SNCM630. Also, the cold-rolled steel plate is preferably SPCC, SPCD, SPCE or SPCEN.

The steel material making up the sliding surfaces 100 and 101 has the austenite phase as one of the Fe—C phases of steel. The austenite phase exists as a multiplicity of crystal particles in the neighborhood of the sliding surfaces 100 and 101, and is preferably distributed among the other Fe—C phases (for example, martensite phase). This austenite phase is what is called the retained austenite not converted to martensite after hardening of the steel material.

In the neighborhood of the sliding surfaces 100 and 101, the other Fe—C state than austenite is preferably the martensite phase for the most part.

The above-mentioned steel material preferably has one or a plurality of elements selected from the group of C, N, Mn, Ni and Pd as elements generating austenite phase. By adjusting the content of the elements generating austenite phase in the steel material, a predetermined amount of retained austenite can be obtained.

According to this embodiment, the austenite phase is distributed in the neighborhood of the sliding surfaces 100 and 101 of the thrust bearing 53, and therefore, the abrasion loss of the sliding surfaces is reduced. The reason is described below.

The thrust bearing 53 is used in the boundary or the mixed lubrication region at the time of activation or “liquid back”. Therefore, the sliding surfaces 100 and 101 are partially or wholly in contact with each other, and the austenite phase of the contacted portions thereof is rapidly strain-hardened. This strain hardening occurs in a part of the crystal particles of the austenite phase. As a result, the hardened part of the crystal particles is not easily worn on the one hand, and the austenite phase not strain-hardened around the particular portion forms a cushion to prevent the wear of the sliding surfaces 100 and 101.

Also, even in the case where foreign matter such as dust intrudes between the sliding surfaces 100 and 101 and the boundary or mixed lubrication occurs, the sliding surfaces 100 and 101 are similarly prevented from being worn.

The retained austenite amount in the neighborhood of the sliding surfaces 100 and 101 is not less than 5 volume %, preferably 5 to 40 volume % or more preferably 5 to 20 volume %.

The fact that the retained austenite amount is not less than 5 volume % effectively reduces the wear of the sliding surfaces 100 and 101. The retained austenite amount of the sliding surfaces 100 and 101 may change due to the rise of the temperature of the sliding surfaces or the stress acting on the sliding surfaces while the scroll compressor 11 is in operation. At the time of fabrication of the scroll compressor 11, therefore, the retained austenite amount in the neighborhood of the sliding surfaces 100 and 101 is set to a value which is maintained at not less than 5 volume % over the entire service life of the scroll compressor 11.

In the case where the retained austenite amount is 40 volume % or more, on the other hand, the hardness of the sliding surfaces 100 and 101 is reduced and the abrasion loss is increased undesirably. This is due to the low hardness of the austenite phase as compared with the martensite phase.

The areas of the first and second sliding surfaces 100 and 101 where the retained austenite amount is not less than 5 volume % extend to a depth not less than 10 μm or preferably 10 to 200 μm from the surface. Further, the areas where the retained austenite amount is not less than 5 volume % may cover the whole of the scroll-side plate 53a and the housing-side plate 53b.

In the case where the running-in operation is performed before using the scroll compressor 11, for example, the areas of the first and second sliding surfaces 100 and 101 where the retained austenite amount is not less than 5 volume % after running-in are preferably not less than 10 μm deep from the surface.

The retained austenite amount on each of the two sliding surfaces 100 and 101 can be measured by using a well-known method. For example, the peak ratio between a (ferrite) phase and γ (austenite) phase obtained by X-ray measurement can be used.

In order to obtain the two sliding surfaces 100 and 101 having the retained austenite amount in the aforementioned range in the neighborhood of the surface, the steel material is preferably subjected to the hardening process, tempering process, carburizing process, nitriding process or carbonitriding process. The well-known conditions can be used for heat treatment.

In each of the processes described above, first, the scroll-side plate 53a and the housing-side plate 53b are preferably machined to the shape of a predetermined size from a steel material, and then finish machined.

The carburizing process includes the solid carburizing process, liquid carburizing process, gas carburizing process and the vacuum carburizing process as well known.

In place of the carburizing process, the steel material may be preferably subjected to the nitriding process. A well-known nitriding process uses ammonia or nitride. The nitrogen content in the neighborhood of the sliding surfaces 100 and 101 after the nitriding process is preferably in the range described above.

Further, in order to execute the nitriding process together with the carburizing process on the steel material, the carbonitriding process is preferably used. In the carbonitriding process, for example, the steel material is subjected to the nitriding process in the carburizing atmosphere.

In the process for increasing the content of carbon or nitrogen in the neighborhood of the steel material surface, the retained austenite amount in the neighborhood of the surface is adjusted to the aforementioned range on the one hand and the hardness in the neighborhood of the steel material surface is increased while at the same time maintaining the internal mildness on the other hand. Therefore, this process is desirable for improving the wear resistance and fatigue resistance of the scroll-side plate 53a and the housing-side plate 53b formed of the steel material.

In the scroll compressor 11 according to this embodiment, the thrust bearing 53 contains the austenite phase of a predetermined content in the neighborhood of the sliding surfaces 100 and 101, and therefore, the wear resistance is improved. Even in the case where the sliding bearing 53 is used in the boundary or the mixed lubrication region at the time of activating or “liquid back” of the scroll compressor 11, therefore, the sliding surfaces 100 and 101 are less worn, and the performance of the scroll compressor is not substantially deteriorated. Also, this scroll compressor requires no complicated control operation and is not high in cost.

Also, according to this embodiment, the sliding surfaces 100 and 101 of the thrust bearing 53 each have a portion to a predetermined depth from the surface thereof where the austenite phase is hardened for an improved wear resistance. Even in the case where the thrust bearing 53 is used in the boundary or the mixed lubrication region and the sliding surfaces 100 and 101 are worn, therefore, the functions of the thrust bearing 53 can be positively maintained for a predetermined length of time.

Also, according to this embodiment, the surface roughness of the sliding surface pair 100 and 101 is so low that the use in the boundary or the mixed lubrication region is accompanied by only a small wear of the sliding surfaces 100 and 101 for an improved anti-seizure property.

Also, according to this embodiment, the bottom surface of the grooves 85 has a large roughness, and therefore, the lubricating oil can be positively held on the rough surface. Even in the case where the scroll compressor 11 is operated with the oil supply to the sliding surfaces of the thrust bearing 53 suspended temporarily, therefore, the sliding surfaces can be sufficiently lubricated by the oil held on the bottom surface of the grooves 85.

Also, in view of the fact that the plurality of the grooves 85 are formed in a network pattern and the pressure receiving portions 83 surrounded by the grooves 85 are each formed in the shape of an island. Thus, the pressure receiving portions 83 are each surrounded by the grooves over the entire periphery thereof, and an oil film 86 can be formed by the wedge effect from all the directions as the result of the revolving motion of the movable scroll 32. Further, the intersections of the plurality of the grooves 85 have a larger width than the remaining portions, and therefore, the oil can be supplied to a sufficiently extent over the plurality of the grooves 85.

Also, the pressure receiving portions 83, which are formed substantially in the shape of an island and arranged in staggered fashion, can be arranged in high density. As a result, the size of the oil film portion per unit area can be increased to support a heavier load.

Also, the grooves 85, being formed on the scroll-side plate 53a fixed on the movable scroll 32, move relatively to the shaft 21 with the revolution of the movable scroll 32. As a result, the oil held on the bottom surface of the grooves 85 is readily supplied to the sliding surfaces in spray.

Next, with reference to FIG. 6, an explanation is given concerning the relative positions of the pressure receiving portions 83 arranged on the scroll-side plate 53a and the housing-side plate 53b with the orbiting motion of the movable scroll 32. FIG. 6 is a diagram showing the manner in which the scroll-side plate 53a moves within the cylindrical case 13a with the orbiting of the movable scroll 32. With the orbiting motion of the movable scroll 32, the scroll-side plate 53a takes the positions (a), (b), (c) and (d) in that order. Let H be the envelope plotted by the inner peripheral edge 53c of the housing-side plate 53b in accordance with the relative motion of the scroll-side plate 53a and the housing-side plate 53b. The plurality of the pressure receiving portions 83 are arranged only on radially outside the envelope H on the scroll-side plate 53a. Even in the case where the movable scroll 32 moves by orbiting, therefore, the pressure receiving portions 83 are not displaced out of the housing-side plate 53b, and a sufficient oil film is formed by the oil held by the plurality of the grooves 85.

Incidentally, the envelope H according to this embodiment is a circle larger than the inner peripheral edge 53c of the housing-side plate 53b by an amount equal to the radius of revolution of the movable scroll 32.

Fifth Embodiment

Next, the scroll compressor 11 according to a fifth embodiment of the invention is explained. The fifth embodiment is different from the fourth embodiment in the configuration of the sliding surfaces 100 and 101 and similar to the fourth embodiment in the other points.

In the scroll compressor 11 according to the preferred fifth embodiment of the invention, the hardness of the second sliding surface 101 of the thrust bearing 53 is higher than that of the first sliding surface 100. Also, the Vickers hardness of the two sliding surfaces 100 and 101 is not less than 500 HV, or preferably, not less than 700 HV.

The Vickers hardness of the first sliding surface 100 is preferably 700 to 850 HV, while the Vickers hardness of the second sliding surface 101 is preferably 1500 to 2500 HV.

The thrust bearing 53 according to this embodiment is explained further below.

The scroll-side plate 53a and the housing-side plate 53b making up the thrust bearing 53 are preferably formed of a steel material like in the embodiments described above.

The housing-side plate 53b constituting the second sliding surface 101 may be formed of a steel material as it is or a steel material increased in hardness by the hardening or film-forming process. The steel material forming the second sliding surface 101, if used as it is for the second sliding surface 101, is preferably higher by at least 500 HV in Vickers hardness than the steel material forming the first sliding surface 100.

In the case where the hardness in the neighborhood of the second sliding surface 101 is increased by the surface treatment such as hardening, the depth from the surface of the particular portion increased in hardness, i.e. the area at least 500 HV higher in Vickers hardness than the first sliding surface 100 is preferably not less than 10 μm or more preferably 10 to 200 μm. Further, the Vickers hardness of the whole housing-side plate 53b may be different from that of the first sliding surface 100 by not less than 500 HV.

The surface treatment described above includes the hardening, carburizing, nitriding or carbonitriding as explained above in the fourth embodiment. The method of surface treatment of the steel material is similar to that described in the fourth embodiment.

In the case where the hardness in the neighborhood of the second sliding surface 101 is increased by the film-forming process, on the other hand, the thickness of the film thus formed is preferably 1 to 5 μm.

The types of the film formed on the second sliding surface 101 preferably include a chromium nitride (CrN) film, a diamond-like carbon (DLC) film and a titanium nitride (TiN) film.

The chromium nitride (CrN) film or the diamond-like carbon (DLC) film can be formed on the second sliding surface 101 by such a well-known method as PVC or CVD.

In the scroll compressor 11 according to this embodiment described above, the Vickers hardness of the second sliding surface 101 of the thrust bearing 53 is at least 500 HV higher than that of the first sliding surface 100. Even in the case where the sliding bearing 53 is used in the boundary or the mixed lubrication region at the time of starting or “liquid back” of the scroll compressor 11, therefore, the second sliding surface 101 develops only a small, shallow dent. As a result, the abrasion loss of the second sliding surface 101 is small, and therefore, the performance of the scroll compressor 11 is not substantially reduced.

Also, according to this embodiment, the hardness of the second sliding surface 101 can be increased appropriately in keeping with the operating conditions of the thrust bearing 53 by the surface treatment such as hardening or the film-forming process described above. Specifically, by adjusting the conditions for surface treatment, an area having the desired hardness can be formed to a predetermined depth from the second sliding surface 101. Also, by adjusting the conditions for the film-forming process, a film having the desired hardness and a predetermined thickness can be formed on the second sliding surface 101.

The scroll compressor 11 according to the fourth or fifth embodiment described above can be used under various operating conditions suited to a particular application. Especially, the thrust bearing 53 of the scroll compressor 11 is desirably used exclusively in the fluid lubrication region to secure the durability thereof.

From this viewpoint, in the scroll compressor 11 according to each of the embodiments described above, the sliding surfaces 100 and 101 of the thrust bearing constituting the sliding bearing 53 are supplied with a mixed fluid containing the lubricating oil and the refrigerant, while the sliding speed of the pressure receiving portions 83 with respect to the second sliding surface 101 is set to not lower than 0.5 m/sec. Then, the load of 0.5 to 20 MPa in average contact pressure is imposed on the pressure receiving portions 83, and the kinematic viscosity of the mixed fluid in operation is maintained at 0.1 to 10 cst. The lubricating oil is desirably contained in the oil described above.

The operating conditions of this scroll compressor 11 are further explained. In the scroll compressor 11 according to each of the embodiments described above, the mixed fluid is supplied to the sliding surfaces 100 and 101 of the thrust bearing 53 by the oil supply means.

Also, with the orbiting of the movable scroll 32, the first sliding surface 100 fixed on the movable scroll 32 slides with respect to the second sliding surface 101 fixed on the middle housing 15. This sliding speed with the second sliding surface 101 is not less than 0.5 m/sec or preferably 0.6 to 5 m/sec.

Also, in this thrust bearing 53, a load is imposed on the pressure receiving portions 83 toward the second sliding surface 101 by the difference between the reaction force of the compressed refrigerant and the force in thrust direction due to the pressure on the movable scroll back surface 32a. The average contact pressure of the pressure receiving portions 83 under this load is 0.5 to 20 MPa or preferably 2 to 15 MPa.

Further, the kinematic viscosity of the mixed fluid on the sliding surfaces 100 and 101 of the thrust bearing 53 under the operating conditions of the scroll compressor 11 described above is 0.1 to 10 cst, or preferably, 4 to 10 cst, where 1 cst equals about 1×10⁻⁶ m²/sec.

By using the scroll compressor 11 according to each of the embodiments described above under the operating conditions described above, an oil film is formed between the pressure receiving portions 83 and the second sliding surface 101 in opposed relation to the pressure receiving portions 83, and therefore, the thrust bearing 53 can be used exclusively in the state of hydrodynamic lubrication. As a result, the wear of the thrust bearing is prevented and the performance of the scroll compressor 11 can be maintained for a long service life.

The preferred embodiments of the invention are explained above, and the invention is not limited to such embodiments.

Although the pressure receiving portions 83 are each substantially circular in the embodiments described above, the pressure receiving portions 83 may alternatively be, for example, oblong, elliptic, triangular, rectangular or otherwise polygonal. Also, each of the pressure receiving portions 83, though formed substantially in a circle and in staggered fashion in the aforementioned embodiments, may alternatively be formed in the shape of a cocoon or linearly.

Also, according to the fourth embodiment described above, the portion where the amount of the retained austenite is not less than 5 volume % covers the whole of the first sliding surface 100. As an alternative, the portion with the retained austenite amount of not less than 5 volume % may be only in the neighborhood of the surface of the pressure receiving portions 83.

Further, according to the fifth embodiment described above, the first and second sliding surfaces 100 and 101 may be both formed of a steel material and the retained austenite amount in the neighborhood of the sliding surfaces 100 and 101 may be not less than 5 volume %.

According to the embodiments described above, the outer peripheral seal portion 81, the pressure receiving portions 83 and the grooves 85 are formed on the scroll-side plate 53a. The invention, however, is not limited to this configuration, and they may be formed on the fixed-side sliding surface 53b of the scroll accommodation depression 31. In other words, the second sliding surface 101 may be fixed on the movable scroll 38.

Also, according to the embodiments described above, an oil supply means is employed to supply the oil to the thrust bearing 53 taking advantage of the pressure difference between the oil separated by the oil separator 63 and the portion where the thrust bearing 53 is arranged. Nevertheless, the invention is not limited to this configuration, and any other configuration whereby the oil is led to the thrust bearing 53 may be used and the oil supply means is not necessarily required to utilize the pressure difference.

The requirements of any one of the embodiments described above may be replaced with the corresponding requirements of any other other embodiments appropriately.

EXAMPLES

The operational effects of the sliding surfaces 100 and 101 of the scroll compressor 11 according to the invention are further explained with reference to examples of the invention and comparative examples for comparison with this invention. The invention, however, is not limited to these examples.

Example 1

The first example is produced by using SUJ2 (nitriding hardening-tempering process) as a test piece of the scroll-side plate 53a having the first sliding surface 100, and similarly, by using SUJ2 (nitriding hardening-tempering process) as a test piece of the housing-side plate 53b having the second sliding surface 101. The retained austenite amount in the neighborhood of the first sliding surface 100 is 10 volume %, while the retained austenite amount in the neighborhood of the second sliding surface 101 is also 10 volume %. These retained austenite amounts are measured by the method described above.

Example 2

The second example is produced similarly to the first example by using SCr415 (carbonitriding hardening process) as a test piece of the scroll-side plate 53a having the first sliding surface 100, and by using SUJ2 (hardening-tempering process) as a test piece of the housing-side plate 53b having the second sliding surface 101. The retained austenite amount in the neighborhood of the first sliding surface 100 is 8 volume %, while the retained austenite amount in the neighborhood of the second sliding surface 101 is 10 volume %.

Example 3

As a test piece of the scroll-side plate 53a having the first sliding surface 100, SUJ2 (nitriding hardening-tempering process) is used, while as a test piece of the housing-side plate 53b having the second sliding surface 101, SUJ2 (nitriding hardening-tempering process) is used. Then, a CrN film is formed to the thickness of 3±1 μm on the second sliding surface 101. In this way, the third example is obtained.

The Vickers hardness of the first sliding surface 100 is 700 HV, the Vickers hardness of the second sliding surface 101 is 1500 HV, and the difference of Vickers hardness between the two sliding surfaces is 800 HV.

Example 4

Except that a DLC film is formed to the thickness of 2±1 μm on the second sliding surface 101, the fourth example is obtained similarly to the third example.

The Vickers hardness of the first sliding surface is 700 HV, the Vickers hardness of the second sliding surface 101 is 2000 HV, and the difference of Vickers hardness between the two sliding surfaces is 1300 HV.

Comparative Example 1

The first comparative example is produced similarly to the first example by using SK5 (hardening-tempering process) as a test piece of the scroll-side plate 53a having the first sliding surface 100, and by using SUJ2 (hardening-tempering process) as a test piece of the housing-side plate 53b having the second sliding surface 101. The retained austenite amount in the neighborhood of the first sliding surface 100 is 4 volume %, while the retained austenite amount in the neighborhood of the second sliding surface 101 is 10 volume %. The Vickers hardness of the first sliding surface 100 is 650 HV, the Vickers hardness of the second sliding surface 101 is 700 HV, and the difference of Vickers hardness between the two sliding surfaces is 50 HV.

[Evaluation of Abrasion Loss]

With reference to the first to fourth examples and the first comparative example described above, the abrasion loss is evaluated as described below.

The abrasion loss is evaluated using the barbell plate tester shown in FIG. 18. The barbell plate tester includes a barbell 103 with a pair of disks fixed on a cylindrical shaft in spaced relationship to each other and a plate 104 with the barbell mounted thereon.

The pair of the disks is each fabricated from a test piece of the housing-side plate 53b and the plate 104 is fabricated from the test piece of the scroll-side plate 53a as a combination (hereinafter referred to also as a set A). Similarly, the pair of the disks is each fabricated from a test piece of the scroll-side plate 53a and the plate 104 is fabricated from the test piece of the housing-side plate 53b as a combination (hereinafter referred to also as a set B).

Each disk of the disk pair is 14 mm in outer diameter and 5 mm thick. The distance between the pair of the disks of the barbell 103 is 21 mm. The four sides of the plate 104 each have the length of 30 mm, and the thickness of the plate 104 is 1.5 to 6 mm, which is varied from one test piece to another.

The plate 104 is immersed in the lubricating oil, and the sliding surfaces between the barbell 103 and the plate 104 are also immersed in the lubricating oil. The test is conducted in such a manner that with a predetermined load imposed on the barbell 103 from above, the plate 104 is rotated at a predetermined rotational speed for a predetermined time, after which the abrasion loss of the test pieces of the barbell 103 and the plate 104 is measured.

A plurality of the measurement conditions combining the load and the rotational speed are used. Also, the measurement conditions are appropriately adjusted for each test piece. Specifically, the load is in the range of 0 to 1000 N (0 to 500 MPa in contact pressure), and the rotational speed in the range of 0 to 2000 rpm (0 to 2 m/sec in sliding speed).

First, the specific abrasion loss of the first example is measured as described below.

The measurement is conducted a plurality of times for different products of contact pressure and sliding distance using the barbell plate tester thereby to measure the abrasion loss of the test piece of the barbell 103 and the abrasion loss of the test piece of the plate 104. The sliding distance is determined from the product of the rotational speed and time. The abrasion loss is assumed to be the volume reduced by the wear of the test piece. The measurement is conducted for the set A and the set B of the first example. The barbell 103 and the plate 104 are lubricated in boundary.

The measurement result is plotted with the product of the contact pressure and the sliding distance as an abscissa and the abrasion loss as an ordinate, and from the inclination of the curve, the specific abrasion loss is determined. The specific abrasion loss is determined for each of the first and second sliding surfaces 100 and 101.

Next, the estimated abrasion loss according to the first example is determined as described below. The estimated abrasion loss is a value of the abrasion loss estimated for an actual machine using the specific abrasion loss.

Using the contact pressure and the sliding distance of the thrust bearing 53 in the operation of an actual machine under predetermined conditions, the abrasion loss A under the boundary lubrication conditions is determined from the product of specific abrasion loss, contact pressure and the sliding distance. Taking the oil film parameter into consideration, the estimated abrasion loss in the mixed lubrication state is determined from the abrasion loss A. The estimated abrasion loss is determined for each of the first and second sliding surfaces 100 and 101.

The estimated abrasion loss is determined similarly for the second to fourth examples and the first comparative example. The result is shown in Table 1.

	TABLE 1
	Example	Comparative
	1	2	3	4	Example 1
Austenite	First	10	8	—	—	4
amount in	sliding
volume %	surface
	Second	10	10	—	—	10
	sliding
	surface
Vickers hardness		800	1300	50
difference HV
Estimated	First	0.35	0.40	0.20	0.20	6.0
abrasion	sliding
loss in μm	surface
	Second	0.40	0.50	0.00	0.00	2.00
	sliding
	surface
	Total	0.75	0.90	0.20	0.20	8.0

The estimated abrasion loss according to the first to fourth examples, as shown in Table 1, is known to be smaller than that of the first comparative example. Especially, the abrasion loss is minimal and wear resistance high in the third and fourth examples.

Sixth Embodiment

The sixth embodiment of the invention will be explained below with reference to FIGS. 19 to 25. The components similar to or identical with those of the embodiments described above are designated by the same reference numerals, respectively.

FIG. 19 is a longitudinal sectional view showing the scroll compressor 11 according to the sixth embodiment. A compressor operated in a refrigeration circuit using the carbon dioxide refrigerant with the pressure of the discharged carbon dioxide exceeding the critical pressure is explained as an example. The invention, however, is not limited to this configuration.

The scroll compressor 11 according to this embodiment is a motor driven hermetic compressor accommodating a motor unit 27 and a compression mechanism 10 in a closed container 13.

The closed container 13 includes a cylindrical case 13a, a motor-side end case 13b assembled at the ends of the cylindrical case 13a and a compression mechanism-side end case 13c.

The motor unit 27 includes a stator 25 fixed on the inner peripheral surface of the cylindrical case 13a and a rotor 23 fixed on the shaft 21 rotationally driven by the motor unit 27.

The compression mechanism 10 includes a bearing member 15 fixed at a position adjacent to the stator 25 in the cylindrical case 13a, a movable scroll 32 orbited by the crank mechanism 28 supported on the main bearing 17 arranged on the bearing member 15, and a fixed scroll 38 fixed on the cylindrical case 13a in opposed relation to the movable scroll 32 to form a compression chamber 45, described later, together with the movable scroll 32.

The shaft 21 is supported horizontally by the auxiliary bearing 19 fixed on the discal support member 14 arranged in the vicinity of the motor-side end case 13b and the main bearing 17.

The movable scroll 32 includes a discal movable-side plate 33, a movable-side spiral blade 41 erected in an involute curve toward the fixed scroll 38 from the end surface of the movable-side plate 33, and a boss 35 erected cylindrically toward the bearing member 15 from the end surface of the movable-side plate 33 far from the movable-side spiral blade 41.

The fixed scroll 38 includes a fixed-side plate 39 fixed on the cylindrical case 13a, and a fixed-side spiral blade 43 arranged in an involute curve on the end surface of the fixed-side plate 39 near to the movable scroll 32.

The bearing member 15 assumes the shape of a triple-cylinder with the diameter thereof progressively increased toward the fixed scroll 39 from the motor unit 27. The small-diameter cylindrical portion 15a near to the motor unit 27 makes up a main bearing 17, the middle-diameter cylindrical portion 15b adjacent to the small-diameter cylindrical portion 15a makes up a crank chamber 29 for accommodating the crank mechanism 28, and the large-diameter cylindrical portion 15c near to the fixed scroll 38 makes up a scroll accommodation unit 31 for accommodating the movable scroll 32 therein while at the same time being fixed by a fixing means such as shrink fitting on the inner peripheral surface of the cylindrical case 13a.

The crank mechanism 28 is comprised of a boss 35 of the movable scroll 32 and an eccentric shaft 37 integrally formed at the end portion of the shaft 21 near to the compression mechanism 10. The eccentric shaft 37 is decentered a given amount from the axial center of the main bearing 17 and the auxiliary bearing 19.

An Oldham ring 36 for preventing the rotation of the movable scroll 32 is arranged between the discal portion 15d connecting the large-diameter cylindrical portion 15c and the middle-diameter cylindrical portion 15b making up the bearing member 15 on the one hand and the movable scroll 32 on the other hand. As a result, the movable scroll 32 is permitted only to orbit. In the compression mechanism 10, the compression chamber 45 formed by the movable-side spiral blade 41 and the fixed-side spiral blade 43 in mesh with each other are reduced in volume by the revolution of the movable scroll 32 with respect to the fixed scroll 38, thereby compressing the refrigerant supplied from the intake tube 47 into the intake chamber 46 communicating with the outermost peripheral side of the fixed-side spiral blade 43.

According to this embodiment, the Oldham ring 36, as shown in FIG. 20, includes a pair of first key portions 36b protruded along the normal to one of the surfaces of an annular plate 36a and a pair of second key portions 36c protruded from the other surface thereof. The line segment connecting the pair of the first key portions 36b is orthogonal to the line segment connecting the pair of the second key portions 36c. The first key portions 36b, as shown in FIG. 19, is received in a pair of oblong first key slot portions 42 formed on the back surface 32 of the movable scroll, while the second key portions 36c are received in a pair of oblong second way portions, not shown, formed on the discal unit 15d of the bearing member. The key portions 36b, 36c and the key slot portions 42 are formed in such a manner that the key portions 36b, 36c are fitted and slide within the key slots radially of the Oldham ring 36.

The movable scroll 32 is subjected to the axial force (in this embodiment, the force pushing the movable-side plate 33 toward the discal portion 15d from the fixed scroll 38 side) received by the movable-side plate 33 due the difference between the reaction force of the compressed refrigerant and the force along the thrust direction under the pressure on the back surface 32 of the movable scroll. In order to orbit the movable scroll while at the same time stably supporting this axial force (thrust), a thrust support surface 15e is formed at the end surface of the discal portion 15c in opposed relation to the movable scroll 32, while a sliding surface 34a adapted to slide in contact with the thrust support surface 15e is formed on the back surface 32 of the movable scroll.

A discharge port 49 is formed axially through the fixed-side plate 39 at the central portion of the fixed-side spiral blade 43, and the refrigerant compressed by the movable scroll 32 and the fixed scroll 38 is discharged into the discharge chamber 50 from the discharge port 49.

The high-temperature high-pressure refrigerant discharged into the discharge chamber 50 is led to the centrifugal oil separator 63 through the refrigerant path 57 extending upward from the discharge chamber 50. The refrigerant that has flowed into the oil separator 63, after being centrifugally separated from the oil contained in the refrigerant, is sent to an external refrigerant circuit through the discharge tube 59.

The oil that has been separated by the oil separator 63, on the other hand, is moved downward under gravitation and stored in the high-pressure oil storage 65 through the small-diameter hole 64.

The oil relatively high in pressure that has been stored in the high-pressure oil storage 65 is led to the oil path 69 formed in the movable-side plate 33 by way of the oil return path 47 formed through the fixed-side plate 39. Then, through the oil path 69, the oil flows into the space between the end portion of the shaft 21 and the bottom surface of the boss 35, and further, into the oil path 71 formed axially through the shaft 21.

Part of the oil that has flowed into the oil path 71 flows into the shaft groove 21a formed on the shaft 21 from a diametrical hole 71a, and after lubricating the main bearing 17, the crank mechanism 28, the thrust support surface 15e and the sliding surface 34a, reaches the scroll housing unit 31. Incidentally, the middle-diameter cylindrical portion 15b is formed with an oil groove 72 for establishing communication between the diametrical hole 71a and the thrust support surface 15e above the shaft 21 to lead the oil to the thrust support surface 15e above the shaft 21.

Also, part of the oil that has flowed leftward in FIG. 19 through the oil path 71 lubricates the auxiliary bearing 19, while major part of the oil drops into the low-pressure oil storage 66 expanding downward of the whole internal area of the closed container 13 from the end of the oil path 71. The oil stored in the low-pressure oil storage 66 reaches the scroll housing unit 31 through the oil return hole 73 formed in the lower part of the bearing member 15, and being supplied to the sliding surfaces of the movable scroll 32 and the fixed scroll 38, compressed together with the refrigerant in the compression chamber 45.

Next, with reference to FIG. 21, the back surface 32 of the movable scroll is explained in detail. According to this embodiment, the back surface of the movable scroll has a circular contour of which the central portion is formed with a boss 35 coupled with an eccentric shaft 37 (not shown). An annular sliding surface 34a hatched in FIG. 21 is formed radially outward of the center line of the boss 35, and a depressed surface 34b lower in level than the sliding surface 34a is formed in the area between the sliding surface 34a and the boss 35 (this depressed surface, not in contact with the thrust support surface 15e of the bearing member, is hereinafter referred to as the non-contact surface 34b). Also, the pair of the oblong first key slot portions 42 are formed on the non-contact surface 34b so that the radially outward end thereof may be in contact with the inner peripheral edge of the sliding surface 34a. As a result, the area adjacently in contact with the first key slot portion 42, except for the area adjacent to the radial outer end of the center line, constitutes the non-contact surface 34b in its entirety.

In the case where the sliding surface 34a is formed in this way, as shown by a in FIG. 26, a corner portion adjacent to the first key slot portion 42 is not formed, and therefore, the generation of an area where the contact pressure is locally high and which is liable to cut the oil film is suppressed. Incidentally, the radially outward end of the first key slot portion 42, though in contact with the inner peripheral edge of the sliding surface 34a according to the aforementioned embodiments, may be completely spaced from the sliding surface 34a according to this invention.

Seventh Embodiment

Next, the sliding surface 34a of the movable scroll according to the seventh embodiment will be explained with reference to FIG. 22. The sliding surface 34a according to this embodiment, though annular, has an internal peripheral boundary not circular but substantially elliptic. As a result, the sliding surface 34a is formed in such a manner that the diameter L₁ of the boundary line in the first direction to connect the pair of the first key slot portions (vertical direction in FIG. 22) is larger than the diameter L₂ of the boundary line in the direction perpendicular to the first direction (horizontal direction in FIG. 22).

Eighth Embodiment

Next, the sliding surface 34a of the movable scroll according to the eighth embodiment will be explained with reference to FIG. 23. The greater part of the inner peripheral boundary of the sliding surface 34a according to this embodiment is circular and passes inside of the radially outer end of the first key slot portions 42. The boundary line of the portion in contact with the pair of the first key slot portions 42, however, merges with the arc of the first key slot portions 42 as a tangential line T_L at about 45 degrees to the line segment connecting the pair of the first key slot portions 42 according to this embodiment.

Ninth Embodiment

Next, the sliding surface 34a of the movable scroll according to the ninth embodiment will be explained with reference to FIG. 24. The sliding surface 34a according to this embodiment is comprised of an annular sliding surface 34a₁ formed on the outer peripheral edge of the back surface 34 of the movable scroll, a plurality of first insular sliding surfaces 34a₂ formed radially inside of the annular sliding surface 34a₁ and a plurality of second insular sliding surfaces 34a₃ smaller in diameter than the first insular sliding surfaces 34a₂. The top of the first and second insular sliding surfaces 34a₂, 34a₃ and the top of the annular sliding surface 34a₁ are flush with each other. The first and second insular sliding surfaces 34a₂, 34a₃ are in spaced relation with each other and the annular sliding surface 34a₁. The lubricating oil can thus flow through the gaps or the grooves formed by the spaced relation. Also, according to this embodiment, the first key slot portions 42 are in the shape of a rectangle having four arcuate corners, and each have a radially outward end in spaced relation with the sliding surface (annular sliding surface 34a₁).

Although the sliding surface contains an annular sliding surface in this embodiment, the sliding surface may alternatively be comprised of insular sliding surfaces.

Tenth Embodiment

Next, the tenth embodiment will be explained with reference to FIG. 25. FIG. 25 will be a diagram showing the surface of the bearing member on the side in opposed relation to the movable scroll. This surface is comprised of an end surface 15f of a large-diameter cylindrical portion 15c on the outermost periphery, a circular crank chamber 29 at the central portion, a thrust support surface 15e adjacent to the end surface 15f of the large-diameter cylindrical portion 15c, and a bearing member-side non-contact surface 15g depressed and lower in level than the thrust support surface 15e inside of the thrust support surface 15e, while a pair of oblong second key slot portions 42 are formed on the non-contact surface 15g. The inner peripheral edge of the thrust support surface 15e, though arcuate for the most part, is not arcuate and tangentially merges with the arc of the radially outer end of the second key slot portions 42 at about 30 degrees in the neighborhood of the second key slot portions 42. As a result, the area adjacent to the second key slot portions 42, except for the area adjacent to the radially outer end described above, constitutes the non-contact surface 15g in its entirety.

The sliding surface 34a and the thrust support surface 15e according to this invention may assume various shapes other than those shown in the aforementioned embodiments, and the first and second key slot portions are not limited to an oblong or rectangle.

Also, according to the embodiments described above, the back surface of the movable scroll 32 is formed with the sliding surface 34a in sliding contact with the thrust support surface 15e and the non-contact surface 34b not in contact with the thrust support surface 15e inside the sliding surface 34a. Nevertheless, the present invention is not limited to this configuration, but the thrust support surface may be arranged between the movable scroll and the fixed scroll, and the non-contact surface and the sliding surface may be formed on the outer periphery of the spiral blade of the movable scroll.

While the invention has been described by reference to specific embodiments chosen for purposes of illustration, it should be apparent that numerous modifications could be made thereto by those skilled in the art without departing from the basic concept and scope of the invention.

Claims

1. A scroll compressor comprising: a fixed scroll fixed on a housing;a movable scroll arranged in opposed relation to the fixed scroll and adapted to revolve with respect to the fixed scroll on a rotary shaft thereby to compress a fluid; anda thrust bearing for receiving the axial force received by the movable scroll;wherein the thrust bearing includes a plurality of grooves formed on a sliding surface thereof and communicating with each other;wherein areas defined by the plurality of the grooves communicating with each other constitute insular pressure receiving portions independent of each other; andwherein the pressure receiving portions occupy at least one half of the area of the sliding surface.

2. The scroll compressor according to claim 1, wherein the plurality of the grooves are arranged in meshes.

3. The scroll compressor according to claim 2, wherein the insular pressure receiving portions are each substantially circular in shape.

4. The scroll compressor according to claim 2, wherein the insular pressure receiving portions are each polygonal.

5. The scroll compressor according to claim 3, wherein the insular pressure receiving portions are arranged in staggered fashion.

6. The scroll compressor according to claim 1, wherein the entire peripheral edge portion of each of the pressure receiving portions is rounded or tapered.

7. The scroll compressor according to claim 1, further comprising an oil separating means for separating the lubricating oil from the fluid, wherein the lubricating oil is supplied to the thrust bearing by the pressure difference between the lubricating oil separated by the oil separating means and the portion at which the thrust bearing is arranged.

8. The scroll compressor according to claim 1, wherein the fluid is carbon dioxide, and the pressure of the carbon dioxide discharged exceeds the critical pressure thereof.

9. A scroll compressor comprising: a fixed scroll fixed on a housing;a movable scroll arranged in opposed relation to the fixed scroll and adapted to revolve with respect to the fixed scroll on a rotary shaft thereby to compress a fluid;a thrust bearing arranged on the back surface of the movable scroll for receiving the axial force; anda lubricating oil supply means for supplying the lubricating oil to the thrust bearing;wherein the thrust bearing includes a donut-shaped first member formed with a plurality of grooves and a plurality of pressure receiving portions defined by the plurality of the grooves and a donut-shaped second member in sliding contact with the first member, andwherein the plurality of the pressure receiving portions are arranged only on radially outside an envelope plotted by the inner peripheral edge of the second member by the relative motion of the first member and the second member.

10. A scroll compressor comprising: a fixed scroll fixed on a housing;a movable scroll arranged in opposed relation to the fixed scroll and adapted to revolve with respect to the fixed scroll on a rotary shaft thereby to compress a fluid;a thrust bearing arranged on the back surface of the movable scroll for receiving the force in axial direction; anda lubricating oil supply means for supplying the lubricating oil to the thrust bearing;wherein the thrust bearing includes a donut-shaped first member formed with a plurality of grooves and a plurality of pressure receiving portions defined by the plurality of the grooves and a donut-shaped second member in sliding contact with the first member; andwherein the plurality of the pressure receiving portions are arranged only on radially inside an envelope plotted by the outer peripheral edge of the second member by the relative motion of the first member and the second member.

11. The scroll compressor according to claim 9, wherein the plurality of the grooves are arranged in meshes and communicate with each other.

12. The scroll compressor according to claim 11, wherein the intersections of the plurality of the grooves in meshes have a larger groove width than the other parts.

13. The scroll compressor according to claim 12, wherein the insular pressure receiving portions are substantially circular in shape and arranged in staggered fashion.

14. The scroll compressor according to claim 9, further comprising an oil separating means for separating the lubricating oil from the fluid, wherein the lubricating oil supply means supplies the lubricating oil to the thrust bearing by the pressure difference between the lubricating oil separated by the oil separating means and the portion where the thrust bearing is arranged.

15. The scroll compressor according to claim 9, wherein the fluid is carbon dioxide and the pressure of the carbon dioxide discharged exceeds the critical pressure.

16. A scroll compressor comprising: a fixed scroll;a movable scroll adapted to revolve with respect to the fixed scroll on a rotary shaft thereby to compress a fluid; anda thrust bearing for receiving the axial force received by the movable scroll;wherein the thrust bearing includes a first sliding surface having a plurality of insular pressure receiving portions defined by the grooves and independent of each other and a second sliding surface with a substantially flat portion in opposed relation to the pressure receiving portions on the first sliding surface;wherein selected one of the first sliding surface and the second sliding surface is fixed on the movable scroll;wherein the pressure receiving portions each include a sagged portion formed along the peripheral edge of the pressure receiving portion and a flat portion inside the sagged portion;wherein the standard deviation σ1 of the surface roughness of the first sliding surface and the standard deviation σ2 of the surface roughness of the second sliding surface are each not more than 0.08 μm; andwherein the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.05≦W/R≦0.98, where R is the effective radius of the pressure receiving portion and W is the width of the sagged portion to assure that the height of the pressure receiving portion is 1 μm lower than the flat portion.

17. The scroll compressor according to claim 16, wherein in the case where e designates the amount of eccentricity of the center of the movable scroll from the axis of the rotary shaft, the ratio between the effective radius R and the eccentricity e holds the relation 0.8<R/e≦1, and the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.05≦W/R≦0.98.

18. The scroll compressor according to claim 16, wherein in the case where e designates the amount of eccentricity of the center of the movable scroll from the axis of the rotary shaft, the ratio between the effective radius R and the eccentricity e holds the relation 0.6<R/e≦0.8, and the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.1≦W/R≦0.85.

19. The scroll compressor according to claim 16, wherein in the case where e designates the amount of eccentricity of the center of the movable scroll from the axis of the rotary shaft, the ratio between the effective radius R and the eccentricity e holds the relation 0.4<R/e≦0.6, and the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.2≦W/R≦0.6.

20. The scroll compressor according to claim 16, comprising the fixed scroll, the movable scroll adapted to revolve with respect to the fixed scroll on the rotary shaft thereby to compress the fluid, and the thrust bearing for receiving the axial force received by the movable scroll, wherein the amount of eccentricity of the center of the movable scroll from the axis of the rotary shaft is given as e,wherein the thrust bearing includes the first sliding surface having a plurality of insular pressure receiving portions independent of each other and defined by the grooves and the second sliding surface with a substantially flat portion in opposed relation to the pressure receiving portions of the first sliding surface,wherein selected one of the first sliding surface and the second sliding surface is fixed on the movable scroll,wherein the pressure receiving portions each include a sagged portion formed along the peripheral edge of each pressure receiving portion and a flat portion inside the sagged portion,wherein the standard deviation σ1 of the surface roughness of the first sliding surface and the standard deviation σ2 of the surface roughness of the second sliding surface are each not more than 0.08 μm, andwherein the oil film parameter Λ expressed by Equation (1) below satisfies the relation Λ≧3,

21. The scroll compressor according to claim 20, wherein the ratio between the effective radius R and the eccentricity e satisfies the relation 0.8<R/e≦1, and the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.05≦W/R≦0.98.

22. The scroll compressor according to claim 20, wherein the ratio between the effective radius R and the eccentricity e satisfies the relation 0.6<R/e≦0.8, and the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.1≦W/R≦0.85.

23. The scroll compressor according to claim 20, wherein the ratio between the effective radius R and the eccentricity e satisfies the relation 0.4<R/e≦0.6, and the ratio between the width W of the sagged portion and the effective radius R satisfies the relation 0.2≦W/R≦0.6.

24. The scroll compressor according to claim 16, wherein the sliding speed of the pressure receiving portions with respect to the second sliding surface is not less than 0.5 m/sec,wherein the load of 0.5 to 20 MPa in average contact pressure is imposed on the pressure receiving portions through the fluid between the pressure receiving portions and the second sliding surface, andwherein the kinematic viscosity of the fluid in operation is 0.1 to 10 cst.

25. The scroll compressor according to claim 16, wherein the insular pressure receiving portions are in the shape of selected one of substantial circle, oblong, ellipse and substantial polygon, and arranged in selected one of staggered, regular grid, oblique grid and random forms.

26. The scroll compressor according to claim 16, wherein the sagged portion is formed over the entire peripheral edge of the pressure receiving portions.

27. A scroll compressor comprising: a fixed scroll;a movable scroll adapted to revolve with respect to the fixed scroll on a rotary shaft thereby to compress a fluid; anda thrust bearing for receiving the axial force received by the movable scroll;wherein the thrust bearing includes a first sliding surface and a second sliding surface in opposed relation to the first sliding surface,wherein selected one of the first sliding surface and the second sliding surface is fixed on the movable scroll, andwherein each of the first sliding surface and the second sliding surface is formed of a steel material, and the retained austenite amount in the neighborhood of the two sliding surfaces is not less than 5 volume %.

28. The scroll compressor according to claim 27, wherein the thrust bearing includes the first sliding surface having a plurality of insular pressure receiving portions defined by the grooves and independent of each other and the second sliding surface having a substantially flat portion in opposed relation to the pressure receiving portions of the first sliding surface,wherein the pressure receiving portions each includes a sagged portion formed on the peripheral edge of the pressure receiving portion and a flat portion inside the sagged portion, andwherein the standard deviation σ1 of the surface roughness of the first sliding surface and the standard deviation σw of the surface roughness of the second sliding surface are each not more than 0.08 μm.

29. The scroll compressor according to claim 27, wherein a fluid including the lubricating oil is supplied to the sliding surfaces of the thrust bearing,wherein the sliding speed of the pressure receiving portions with respect to the second sliding surface is not less than 0.5 m/sec, andwherein the load of 0.5 to 20 MPa in average contact pressure is imposed on the pressure receiving portions, andwherein the kinematic viscosity of the fluid in operation is 0.1 to 10 cst.

30. The scroll compressor according to claim 27, wherein each of the first sliding surface and the second sliding surface includes an area having the retained austenite amount of not less than 5 volume % in the depth of not less than 10 micrometers from the surface.

31. A scroll compressor comprising: a fixed scroll;a movable scroll adapted to revolve with respect to the fixed scroll on a rotary shaft thereby to compress a fluid; anda thrust bearing for receiving the axial force received by the movable scroll;wherein the thrust bearing includes a first sliding surface and a second sliding surface in opposed relation to the first sliding surface,wherein selected one of the first sliding surface and the second sliding surface is fixed on the movable scroll, andwherein the hardness of the second sliding surface is higher than that of the first sliding surface, and the difference in Vickers hardness between the two sliding surfaces is not less than 500 HV.

32. The scroll compressor according to claim 31, wherein the thrust bearing includes the first sliding surface having a plurality of insular pressure receiving portions independent of each other and defined by grooves and the second sliding surface having a substantially flat portion in opposed relation to the pressure receiving portions of the first sliding surface,wherein the pressure receiving portions each include a sagged portion formed along the peripheral edge of the pressure receiving portions and a flat portion inside the sagged portion, andwherein the standard deviation σ1 of the surface roughness of the first sliding surface and the standard deviation σ2 of the surface roughness of the second sliding surface are each not more than 0.08 μm.

33. The scroll compressor according to claim 31, wherein the fluid containing the lubricating oil is supplied to the sliding surfaces of the thrust bearing, the sliding speed of the pressure receiving portions with respect to the second sliding surface is not less than 0.5 m/sec, the load of 0.5 to 20 MPa in average contact pressure is imposed on the pressure receiving portions, and the kinematic viscosity of the fluid in operation is 0.1 to 10 cst.

34. The scroll compressor according to claim 31, wherein the second sliding surface is increased in hardness by selected one of the hardening process and the film-forming process.

35. The scroll compressor according to claim 27, wherein the hardness of the second sliding surface is higher than that of the first sliding surface, and the difference in Vickers hardness between the two sliding surfaces is not less than 500 HV.

36. The scroll compressor according to claim 34, wherein the first sliding surface and the second sliding surface are each formed of steel material, and the retained austenite amount in the neighborhood of the sliding surfaces is not less than 5 volume %.

37. A scroll compressor comprising: a fixed scroll fixed on a housing;a rotary shaft for transmitting the turning effort;a movable scroll arranged in opposed relation to the fixed scroll and adapted to orbit around a rotary shaft by being coupled to the rotary shaft through an eccentric shaft decentered a predetermined distance from the rotary shaft thereby to compress a fluid in collaboration with the fixed scroll;a bearing member having a thrust support surface in opposed relation to the side plate of the movable scroll for axially supporting the side plate along the axis of the rotary shaft; andan anti-rotation mechanism for preventing the rotation of the movable scroll;wherein the side plate of the movable scroll includes a sliding surface adapted to slide in contact with the thrust support surface and a non-contact surface not in contact with the thrust support surface inside the sliding surface, the non-contact surface having grooves, andwherein the sliding surface and the grooves are in spaced relation or in contact with each other, and the sliding surface, if in contact with the grooves, is formed in such a manner that the area adjacent to the grooves circumferentially around the grooves and the area adjacent to the grooves radially inside the grooves constitute the non-contact surface and also in such a manner that the contour line indicating the inner peripheral edge of the sliding surface is in point contact or smoothly converges with the contour line of the grooves.

38. The scroll compressor according to claim 37, wherein the anti-rotation mechanism is an Oldham ring having key portions axially protruded, and the grooves constitute key slot portions combined with the key portions.

39. The scroll compressor according to claim 37, wherein the sliding surface is substantially annular.

40. The scroll compressor according to claim 39, wherein the back surface of the movable scroll includes a pair of grooves, and the sliding surface is formed in such a manner that the diameter of the inner peripheral edge of the sliding surface in the first direction connecting the pair of the grooves is larger than the diameter of the inner peripheral edge in the second direction perpendicular to the first direction.

41. The scroll compressor according to claim 40, wherein the pair of the grooves is each oblong, andwherein the inner peripheral edge of the sliding surface converges with the oblong arc at the radially outer end of each groove as a tangential line inclined with respect to the longitudinal axis of the oblong.

42. The scroll compressor according to claim 37, wherein the sliding surface at least partially includes a plurality of insular sliding surfaces in spaced relation to each other.

43. A scroll compressor comprising: a fixed scroll fixed on a housing;a rotary shaft for transmitting the turning effort;a movable scroll arranged in opposed relation to the fixed scroll and adapted to orbit with respect to the rotary shaft by being coupled to the rotary shaft through an eccentric shaft decentered a predetermined distance from the rotary shaft thereby to compress a fluid in collaboration with the fixed scroll;a bearing member having a thrust support surface in opposed relation to the side plate of the movable scroll to support the side plate in the axial direction of the rotary shaft; andan anti-rotation mechanism for preventing the rotation of the movable scroll;wherein the surface on the side of the bearing member in opposed relation to the movable scroll includes the thrust support surface and a bearing member-side non-contact surface not in contact with the sliding surface in the thrust support surface, the bearing member-side non-contact surface having grooves; andwherein the thrust support surface and the grooves are in spaced relation or in contact with each other, and the thrust support surface, if in contact with the grooves, is formed in such a manner that the area adjacent to the grooves circumferentially around the grooves and the area adjacent to the grooves radially inside the grooves constitute the bearing member-side non-contact surface and also in such a manner that the contour line indicating the inner peripheral edge of the thrust support surface is in point contact or smoothly converges with the contour line of the grooves.

44. The scroll compressor according to claim 37, wherein the fluid is carbon dioxide and the pressure of the carbon dioxide discharged exceeds the critical pressure.