JPH0849673A - Scroll type fluid machinery - Google Patents

Abstract

PURPOSE:To prevent the occurrence of defective lubrication at the inner side in a radial direction of a thrust support surface formed at a bearing housing through simple structure and simple processing and to reliably prevent the occurrence of wear and the burn of the thrust support surface. CONSTITUTION:The bearing 51 of a drive shaft 4 and the eccentric axis part 41 of a drive shaft 4 are placed in a bearing housing 5, and a revolving part 53 capable of effecting revolving movement of a moving scroll 2 and a thrust support surface 52 to support the back of the moving scroll 2 are provided. Further, an annular oil groove 54 is formed approximately in the central part in a radial direction of the thrust support surface 52. A feed oil passage 55 is formed in such a manner that one end is communicated with a main feed oil passage 42 formed in the drive shaft 4 and the other end is opened to the annular oil groove 54. An oil reservoir 8 disconnected from the annular oil groove 54 and communicated with the revolving part 53 is formed in the part, situated radially inside the annular oil groove 54, of the thrust support surface 52.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid machine mainly used for a refrigerant compressor of a refrigerator or an air conditioner.

[0002]

2. Description of the Related Art A conventional scroll type fluid machine receives a bearing for supporting a drive shaft and an eccentric shaft portion of the drive shaft, as described in, for example, Japanese Patent Application Laid-Open No. 4-241785. A bearing housing having a revolving portion that enables the orbiting movement of the movable scroll is provided with a thrust receiving surface for supporting the back surface of the end plate of the movable scroll, and an annular oil groove is provided substantially at the center in the radial direction of the thrust receiving surface. An oil supply passage having one end communicating with the main oil supply passage provided inside the drive shaft and the other end opening to the annular oil groove is formed in the bearing housing, and oil is supplied from the oil supply passage to the annular oil groove. There is known a structure in which the thrust receiving surface is lubricated.

In this scroll type fluid machine, as shown in FIG. 8, a movable scroll A having a scroll A2 projecting from a mirror plate A1 and a fixed scroll (not shown) having a scroll spirally projecting from a mirror plate are provided. While the scrolls A2 are assembled so as to face each other, a boss portion A3 into which the eccentric shaft portion B1 of the drive shaft B connected to the motor is fitted is formed on the end plate A1 of the movable scroll A to form the movable scroll A. The drive shaft B is interlocked with the rotation of the drive shaft B.

Further, a bearing housing C having a bearing C1 for bearing-supporting the drive shaft B is provided, and the end plate A1 of the movable scroll A is supported by a thrust receiving surface C2 formed on the top surface of the bearing housing C. I am trying.

The bearing housing C is provided with the eccentric shaft portion B1 and the boss portion A3 of the movable scroll A.
The orbiting part C3 is formed to receive the orbiting scroll A so that the orbiting motion of the orbiting scroll C can be eccentrically rotated within the orbiting part C3 by rotationally driving the drive shaft B. I try to make a turning motion.

Further, as shown in FIGS. 8 to 9, an annular oil groove C4 is provided in a substantially radial center portion of the thrust receiving surface C2 of the bearing housing C, and one end of the bearing housing C is provided. By forming an oil supply passage C5 that opens to the annular oil groove C4 and has the other end open to the inner circumferential surface of the bearing C1 and communicates with the main oil supply passage B2 formed in the drive shaft B, the oil supply passage is formed. The oil in the main oil supply passage B2 is supplied to the annular oil groove C4 via C5, and the oil in the annular oil groove is slid relative to the thrust receiving surface C2 by the turning motion of the end plate A1 of the movable scroll A. The space between the end plate A1 and the thrust receiving surface C2 is lubricated by lubrication.

[0007]

By the way, when a scroll type fluid machine is used in a refrigerator, a chlorofluorocarbon (for example, R-22) has conventionally been used as a refrigerant. However, due to environmental problems, the chlorofluorocarbon is restricted from being used. However, the use of an alternative CFC (for example, HFC134a) instead of the conventional CFC is required. In this case, the lubricating oil used for this alternative CFC cannot be the lubricating oil (SUNISO oil) used for the conventional CFC (for example, R-22) because of its compatibility,
Since the ester oil is used as the lubricating oil, there is a problem that the lubricating performance is deteriorated as compared with the conventional lubricating oil.

That is, in the conventional lubricating oil, the annular oil groove C is used.
The length from 4 to the orbiting diameter of the orbiting scroll A was able to be sufficiently lubricated within the orbiting diameter range by the sliding of the orbiting scroll A. Since it is high and rebounds when pressure is applied, insufficient lubrication occurs, and this insufficient lubrication causes various problems.

That is, when the fluid machine is operated, the end plate A1 of the movable scroll A is generated by the internal pressure of each spiral body.
Bends toward the drive shaft B at its center,
As a result, the surface pressure of the thrust receiving surface C2 on the radially inner side increases.

Therefore, even within the range of the turning diameter from the annular oil groove C4, the oil film formed by the ester oil is ruptured inside the thrust receiving surface C2 in the radial direction, resulting in poor lubrication. Due to poor lubrication, the radially inner portion of the thrust receiving surface C2 is worn, and in some cases, seizure may occur, and due to this wear, the thrust receiving surface C2 supporting the end plate A1 may be worn.
The distance between the supporting points at the point A becomes larger, and the distance between the supporting points becomes larger, the bending of the end plate A1 further increases, and a gap is generated between the spiral bodies A2, which deteriorates the sealing performance. However, there was a problem that resulted in performance degradation.

Further, in the refrigerator using the alternative CFC, the differential pressure between the high pressure and the low pressure on the system side is smaller than that in the case of using the conventional CFC, so that
Although the bending amount of the end plate A1 is small, the gap between the thrust receiving surface C2 and the rear face of the end plate A1 becomes narrower as the bending amount decreases, so that the thrust receiving surface C2 from the annular oil groove C4. The oil supply passage is narrowed when the oil is discharged to the tank, and the amount of oil supply is reduced. Furthermore, the ester oil for CFC substitute has a higher viscosity than the conventional suniso oil, and the above passage resistance increases. With that,
The oil supply performance to the thrust receiving surface C2 deteriorates, which also aggravates the problem of poor lubrication.

Further, in the conventional example of the above publication, the end plate A is
In order to reduce the surface pressure on the thrust receiving surface C2 of the end plate A1 on the inner side in the radial direction due to the bending of the end plate 1, as shown in FIG. Forming a taper surface A4 inclined to the anti-thrust receiving surface side, and when the end plate A1 bends to the thrust receiving surface side, the back surface of the end plate A1 is the thrust receiving surface C2.
It is configured to be almost horizontal with respect to. According to this structure, the surface pressure on the radially inner side of the thrust receiving surface C2 can be made small. However, the purpose of forming the tapered surface A4 on the back surface of the thin end plate A1 in this way is to improve the processing accuracy. In other words, there is a problem that the processing becomes difficult, and the problem due to the use of the CFC substitute cannot be basically solved.

Further, when lubricating the thrust receiving surface C2, it is conceivable to form a plurality of oil grooves C6 radially extending in the radial direction as shown in FIG. 10 to supply oil from the inner side to the outer side in the radial direction. However, there is a problem that the oil supply characteristics are worse than those of the annular oil groove and the productivity is also deteriorated.

That is, when the circumferential pitch at the radially inner end of each oil groove C6 is set to the orbiting diameter of the movable scroll A, the circumferential pitch at the radially outer end of each oil groove C6. Becomes larger than the turning diameter, the lubrication on the outer side in the radial direction deteriorates, and poor lubrication occurs, and when the circumferential pitch of the radially outer end of the oil groove C6 is set to the turning diameter. The circumferential pitch at the radially inner end of the oil groove C6 becomes very small, the pressure receiving area at the radially inner side of the thrust receiving surface C2 becomes small, and there arises a problem that sufficient supporting strength cannot be obtained. Therefore, it is less advantageous than the annular oil groove.

The present invention has been made in view of the above problems, and an object thereof is to use a thrust receiving surface formed on a bearing housing with a simple structure while using an annular oil groove without increasing the cost. Prevents poor lubrication on the inside in the radial direction,
An object of the present invention is to provide a scroll type fluid machine capable of reliably preventing abrasion and seizure of the thrust receiving surface.

[0016]

In order to achieve the above object, the invention as set forth in claim 1 receives the bearing 51 of the drive shaft 4 and the eccentric shaft portion 41 of the drive shaft 4 to orbit the movable scroll 2. A bearing housing 5 having a swivel portion 53 for allowing movement is provided with a thrust receiving surface 52 for supporting the back surface of the movable scroll 2, and an annular oil groove 54 is provided at a substantially central portion in the radial direction of the thrust receiving surface 52. In the scroll type fluid machine, the bearing housing 5 is provided with an oil supply passage 55 having one end communicating with the main oil supply passage 42 provided inside the drive shaft 4 and the other end opening to the annular oil groove 54. The thrust receiving surface 52 is blocked from the annular oil groove 54 on the radially inner side of the annular oil groove 54, and the swivel portion 5 is provided.
The oil sump 8 communicating with 3 is provided.

According to the second aspect of the present invention, an annular step portion 56 facing the swivel portion 53 of the bearing housing 5 is formed on the top surface portion of the bearing housing 5 radially inward of the annular oil groove 54. The thrust bearing member 9 having the oil reservoir 8 and the thrust receiving surface 52, which is disconnected from the annular oil groove 54 and communicates with the swivel portion 53, is fixed to the annular step portion 56.

According to a third aspect of the present invention, the annular oil groove 54 is provided.
The oil sump 8 that is cut off and communicates with the turning portion 53 of the bearing housing 5 is formed by a plurality of radially extending grooves 81.

According to a fourth aspect of the present invention, the annular oil groove 54 is provided.
And the turning portion 53 in the bearing housing 5 is cut off.
A plurality of first grooves 81 that communicate with the swirl portion 53 and that extend in the radial direction, and an annular shape that communicates with the first grooves 81 radially outward of the first grooves 81. Second groove 8
It was formed by 2.

[0020]

In the invention according to claim 1, the thrust receiving surface 5
In FIG. 2, the oil reservoir 8 is provided radially inward of the annular oil groove 54 so as to be disconnected from the annular oil groove 54 and communicate with the swivel portion 53. Therefore, oil is returned to the swirl portion 53 from a bearing or the like. The oil is eccentrically rotated by the eccentric shaft portion 41 of the drive shaft 4,
Oil can be supplied to the oil sump 8 by centrifugal force, and the oil can be supplied from the oil sump 8 to the thrust receiving surface 52. Therefore, not only from the annular oil groove 54 to the radially inward side of the thrust receiving surface 52 where lubrication deficiency is most likely, but also to the oil sump 8
The oil can be replenished from the inside as well, the lack of lubrication can be eliminated as a whole, and wear and seizure can be satisfactorily prevented.

As a result, even when the CFC substitute is used, it is possible to prevent the oil film of the lubricating oil used for the CFC substitute from breaking, and it is possible to reliably prevent abrasion and baking due to oil shortage. In addition, since the abrasion can be prevented, it is possible to prevent the support points of the movable scroll 2 from being displaced as in the conventional example, and therefore, the sealing property between the scrolls of each scroll is deteriorated and the performance is prevented from being deteriorated. You can do it.

According to the second aspect of the present invention, the annular step portion 56 is formed on the top surface portion of the bearing housing 5, and the annular step portion 56 is cut off from the annular oil groove 54, and the swivel portion 5 is formed.
Since the thrust bearing member 9 having the oil sump 8 and the thrust receiving surface 52 communicating with the No. 3 is fixed, it is not necessary to form the oil sump 8 by processing the bearing housing 5 having a complicated shape. Since the oil sump 8 is formed in the thrust bearing member 9 provided separately from the housing 5, the oil reservoir 8 can be formed easily, and the thrust bearing member 9 is fixed to the annular step portion 56 of the bearing housing 5. Therefore, the oil sump 8 can be easily formed in the bearing housing 5 and the workability can be improved.

In the invention according to claim 3, the annular oil groove 5
4, the oil reservoir 8 communicating with the swivel portion 53 of the bearing housing 5 is formed by a plurality of grooves 81 extending in the radial direction. Therefore, the reduction of the pressure receiving area of the thrust receiving surface 52 is minimized, and The reservoir 8 can be formed, the oil supply performance on the radially inner side of the thrust receiving surface 52 can be improved, and its lubrication can be improved.

Further, the radial outer side of the thrust receiving surface 52 is supplied with oil from the annular oil groove 54, and the radial inner side is supplied with oil from the annular oil groove 54 and the groove 81. Therefore, when the grooves 81 are formed in the radial direction, it is not necessary to make the circumferential pitch of each groove 81 smaller than the orbiting diameter of the movable scroll 2, and therefore, the pressure receiving area of the thrust receiving surface 52 is sufficiently secured. Therefore, the supporting strength can be maintained.

In the invention according to claim 4, the annular oil groove 5
4 is cut off, and the swivel part 5 in the bearing housing 5 is cut off.
3, the oil reservoir 8 communicating with 3 is communicated with the swivel portion 53,
The diameter of the thrust receiving surface 52 is formed by the plurality of first grooves 81 extending in the radial direction and the annular second groove 82 communicating with the first grooves 81 radially outward of the first grooves 81. Lubrication on the inner side in the direction is performed by oil supply from both the annular oil groove 54 and the oil sump 8, and wear and seizure can be satisfactorily prevented. Since the two grooves 82 are formed radially outward of the first groove 81, the second groove 82 is formed when the fluid machine is stopped.
Oil can be stored in the groove 82, and when the fluid machine is started, the thrust receiving surface 5 is filled with the oil stored in the second groove 82.
Since the inner side in the radial direction of 2 can be lubricated, it is possible to prevent poor lubrication at the time of starting the thrust receiving surface 52.

[0026]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The scroll type fluid machine shown in FIG. 1 is a low pressure dome type scroll type compressor used as a refrigerator, in which a compression element CF is provided above the inside of a hermetic casing 1 and a motor M is provided below the inside of the casing 1. The compression element CF is composed of a movable scroll 2 in which a scroll 22 is projected on a mirror plate 21 and a fixed scroll 3 in which a scroll 32 is projected on a mirror plate 31. While the spiral bodies 22, 32 are combined so as to face each other, the boss portion 2 for fitting the eccentric shaft portion 41 of the drive shaft 4 connected to the motor M to the end plate 21 of the movable scroll 2
3 is formed so that the movable scroll 2 is interlocked with the rotational drive of the drive shaft 4.

Further, a bearing housing 5 having a bearing 51 for bearing-supporting the drive shaft 4 in the casing 1.
Is provided to fix the fixed scroll 3 to the bearing housing 5 and to end the end plate 21 of the movable scroll 2.
Are supported by the thrust receiving surface 52 formed on the top surface of the bearing housing 5.

Further, a partition body 6 is provided inside the casing 1 on the upper side of the fixed scroll 3, and the fixed scroll 3 is formed on the upper side of the partition body 6 by the partition body 6. The discharge port 33 is opened, and the high pressure chamber 12 for opening the external discharge pipe 11 that discharges the discharged refrigerant to the outside of the casing is formed, and the suction pipe 13 is opened at the lower side of the partition body 6 and the compression is performed. The low-pressure chamber 14 in which the element CF and the motor M are arranged is partitioned and formed.

An Oldham ring 15 is arranged on the outer peripheral portion of the lower surface of the movable scroll 2, and the Oldham ring 15 prevents rotation of the movable scroll 2.
The movable scroll 2 is revolved around the fixed scroll 3.

Therefore, the movable scroll 2 revolves around the fixed scroll 3 by the rotation of the drive shaft 4 accompanying the driving of the motor M, and this revolving drive causes the suction pipe 13 to move into the low pressure chamber 14. The sucked low-pressure gas is sucked into the compression chamber formed by the scrolls 22 and 32 of the scrolls 2 and 3, the sucked gas is compressed, and the compressed gas is discharged from the discharge port 33 to the high-pressure chamber. 12
Is discharged to the outside of the casing 1 from the external discharge pipe 11.

At the lower end of the drive shaft 4, there is provided an oil supply pump 7 such as a positive displacement oil pump which communicates with the oil accumulated at the bottom of the casing 1. The oil supply pump 7 is provided at the bottom of the casing 1. The accumulated oil is pumped up into a main oil supply passage 42 formed through the drive shaft 4 in the axial direction, and is supplied to each sliding portion of the bearing housing 5 such as the bearing 51 of the drive shaft 4 and the thrust receiving surface 52. I am trying.

The eccentric shaft portion 41 and the boss portion 23 of the movable scroll 2 are provided in the bearing housing 5.
A swivel portion 53 is formed to receive the orbiting scroll 2 so that the movable scroll 2 can be swung, and the drive shaft 4 is driven to rotate the eccentric shaft portion 41 in the swivel portion 53 so as to be eccentrically rotated. I am trying to make a turning motion.

Further, as shown in FIG. 2, the thrust receiving surface 52 of the bearing housing 5 has an annular shape, and an annular oil groove 54 is provided at a radially intermediate portion of the thrust receiving surface 52.
Is provided.

The annular oil groove 54 formed in the thrust receiving surface 52 shown in FIG.
The orbiting portion 53 is formed at a position larger than the inner diameter of the orbiting portion 53 by the length of the orbiting diameter of the orbiting scroll 2.

A branch passage 43 is formed in the drive shaft 4 so as to branch from the main oil supply passage 42 and open to the inner peripheral surface of the bearing 51 of the bearing housing 5. One end opens into the annular oil groove 54, and the other end opens at a portion of the inner peripheral surface of the bearing 51 facing the opening of the branch passage 43 and communicates with the main oil passage 42 through the branch passage 43. An oil supply passage 55 is formed.

Then, the oil in the main oil supply passage 42 is supplied to the annular oil groove 54 through the oil supply passage 55, and the movable scroll 2 that slides on the thrust receiving surface 52.
By the turning motion of the end plate 21, the oil in the annular oil groove 54 is supplied between the thrust receiving surface 52 and the end plate 21.

In the scroll compressor described above, as shown in FIGS. 1 to 4, the thrust receiving surface 5 is used.
The oil reservoir 8 is provided on the radially inner side of the annular oil groove 54 in FIG. 2 and is cut off from the annular oil groove 54 and communicates with the swivel portion 53.

In the first embodiment shown in FIGS. 1 to 4, as shown in FIG. 4, at the top surface portion of the bearing housing 5,
The annular oil groove 5 is provided radially inward of the annular oil groove 54.
4 is cut off, and the swivel part 5 in the bearing housing 5 is cut off.
3, a ring-shaped thrust bearing having an oil reservoir 8 and a thrust receiving surface 52 which are formed in the annular step portion 56 and which are cut off from the annular oil groove 54 and communicate with the swivel portion 53. The member 9 is fixed by press fitting.

That is, in the first embodiment, when the thickness of the thrust bearing member 9 is set to be the same as the height of the annular step portion 56, the upper surface of the thrust bearing member 9 when press-fitted and fixed to the annular step portion 56. That is, the surface of the movable scroll 2 facing the end plate 21 is flush with the thrust receiving surface 52 of the bearing housing 5 in the radial direction on the thrust receiving surface 52 side. A plurality of grooves 81 are formed which extend and both ends face the inner and outer peripheral surfaces of the thrust bearing member 9.

By press-fitting the thrust bearing member 9 into the annular step portion 56, the radially outer side of each groove 81 is closed by the annular step portion 56 and cut off from the annular oil groove 54. That is, the radially inner end is opened to the swivel portion 53 to form the oil reservoir 8 by the grooves 81.

As described above, since the oil sump 8 which is cut off from the annular oil groove 54 and communicates with the swivel portion 53 is provided radially inward of the annular oil groove 54 on the thrust receiving surface 52, The oil returned from the bearing or the like to the swivel part 53 is supplied to the oil sump 8 by the centrifugal force due to the eccentric rotation of the eccentric shaft part 41 of the drive shaft 4, and the oil is supplied from the oil sump 8 to the thrust receiving surface 52. You can do it.

Therefore, the annular oil groove 5 is located on the radially inner side of the thrust receiving surface 52 where the lack of lubrication is most likely to occur.
It is possible to supply oil not only from No. 4 but also from the oil sump 8, so that insufficient lubrication can be eliminated as a whole, and wear and seizure can be satisfactorily prevented.

As a result, even when the CFC substitute is used, it is possible to prevent the oil film of the lubricating oil used for the CFC substitute from being broken, and it is possible to reliably prevent abrasion and baking due to oil shortage. In addition, since the abrasion can be prevented, it is possible to prevent the support points of the movable scroll 2 from being displaced as in the conventional example, and therefore, the sealing property between the scrolls of each scroll is deteriorated and the performance is prevented from being deteriorated. You can do it.

Further, in the first embodiment, the thrust bearing member 9 in which the oil sump 8 is provided separately from the bearing housing 5 is provided.
The oil reservoir 8 can be easily formed because it is formed by
The thrust bearing member 9 is attached to the bearing housing 5
The oil sump 8 can be formed in the bearing housing 5 only by fixing it to the annular stepped portion 56, and therefore, it is not necessary to form a groove in the bearing housing 5 having a complicated shape,
The oil sump 8 can be easily formed in the bearing housing 5,
Since the workability can be improved, moreover, since the thrust bearing member 9 is provided separately from the bearing housing 5, it is possible to use a wear-resistant material as the material, and by doing so, wear can be prevented more effectively. Can be done.

Further, in the first embodiment, the oil sump 8 is
Since the groove 81 is formed by a plurality of grooves 81 extending in the radial direction, the pressure receiving area of the thrust receiving surface 52 can be reduced as little as possible, and the oil sump 8 can be formed. The lubrication on the other side can be improved.

Further, the radial outer side of the thrust receiving surface 52 is supplied with oil from the annular oil groove 54, and the radial inner side is supplied with oil from the annular oil groove 54 and the groove 81. Therefore, when the grooves 81 are formed in the radial direction, it is not necessary to make the circumferential pitch of each groove 81 smaller than the orbiting diameter of the movable scroll 2, and therefore, the pressure receiving area of the thrust receiving surface 52 is sufficiently secured. Therefore, the supporting strength can be maintained.

Further, in the first embodiment, the oil sump 8 is formed only by the groove 81 extending in the radial direction. However, as in the second embodiment shown in FIG. 5, the thrust bearing surface of the thrust bearing member 9 on the thrust receiving surface side is the same. An annular notch step portion 91 is formed on the radially inner side, and the notch step portion 9 is radially outward from the notch step portion 91.
1 to form a plurality of radially extending grooves 81,
The oil sump 8 is formed by the notch step portion 91 and the radial groove 81.
May be formed.

In this case, since the entire circumference of the thrust receiving surface 52 on the radially inner side can be exposed to the annular oil reservoir 8 formed by the notch step portion 91, the annular notch step portion. It is possible to satisfactorily supply oil to the thrust receiving surface 52 from 91 via the radial groove 81.

Next, the third embodiment will be described with reference to FIGS.
It will be described based on. In the third embodiment, as in the first and second embodiments, the bearing surface of the bearing housing 5 is cut off from the annular oil groove 54 inward of the annular oil groove 54 in the radial direction. An annular step portion 56 facing the swirl portion 53 of the housing 5 is formed, and the oil sump 8 which is cut off from the annular oil groove 54 and communicates with the swirl portion 53 is formed in the annular step portion 56.
Although the thrust bearing member 9 having the thrust receiving surface 52 and the thrust receiving surface 52 is fixed by press fitting, the structure of the oil sump 8 is different from that in each of the embodiments described above.

That is, in the third embodiment, the notch step portion 92 is formed on the entire circumference of the radially outer end portion of the thrust bearing member 9 on the thrust receiving surface 52 side, and the radially inner side portion is provided with the notch step portion 92. A plurality of first ends that communicate with the notch step portion 92 and that the other end faces the inner peripheral surface of the thrust bearing member 9.
By forming a groove 81 and press-fitting the thrust bearing member 9 into the annular step portion 56, a separate annular first portion is cut off from the annular oil groove 54 by the notch step portion 92 and the annular step portion 56. Two grooves 82 are formed, the first groove 81 is communicated with the second groove 82, and the radially inner end of the first groove 81 is opened to the swivel portion 53 to form the first groove 81. 81 and the second groove 82 form the oil reservoir 8 that is cut off from the annular oil groove 54 and communicates with the swivel portion 53.

As described above, in the third embodiment, the oil of the swirl portion 53 is supplied to the first groove 81, and the first groove 81 is supplied.
Oil can be supplied to the thrust receiving surface 52 from
Further, the oil supplied to the first groove 81 is supplied to the annular second groove 82, and the thrust receiving surface 52 can also be supplied from the second groove 82. Therefore, the thrust receiving surface 52 can be lubricated not only from the annular oil groove 54 but also from the oil sump 8 including the first and second grooves 81 and 82, so that better lubrication can be achieved as a whole. It is possible to prevent abrasion and baking.

Further, since the annular second groove 82 in the oil sump 8 is formed radially outward of the first groove 81, when the fluid machine is stopped, the oil is retained in the second groove 82. Can be stored, and when the fluid machine is started, the radially inner side of the thrust receiving surface 52 can be lubricated by the oil stored in the second groove 82, so that the thrust receiving surface 52 is started. Inadequate lubrication can be prevented.

In each of the embodiments, the oil sump 8 is
Although it is formed by the thrust bearing member 9 provided separately from the bearing housing 5, the oil sump 8 may be formed directly on the bearing housing 5.

The oil sump 8 has the thrust receiving surface 52.
It is also possible to form an annular step portion that opens to the swivel portion 53 at the radially inner end portion thereof and form the oil reservoir 8 by this step portion.

[0055]

According to the first aspect of the present invention, the thrust receiving surface 52 is located radially inward of the annular oil groove 54 and is blocked from the annular oil groove 54 and communicates with the swivel portion 53. Since the oil sump 8 is provided, the oil returned from the bearing or the like to the swivel portion 53 is centrifugally supplied to the oil sump 8 by the eccentric rotation of the eccentric shaft portion 41 of the drive shaft 4, and the oil sump 8 From the above, the thrust receiving surface 52 can be refueled. Therefore, not only the annular oil groove 54 but also the oil sump 8 can be supplied to the radially inner side of the thrust receiving surface 52 where the lack of lubrication is likely to occur, and the lack of lubrication can be eliminated as a whole to reduce wear. -Baking can be satisfactorily prevented.

As a result, even when the CFC substitute is used, it is possible to prevent the oil film of the lubricating oil used for the CFC substitute from being broken, and it is possible to reliably prevent abrasion and baking due to oil shortage. In addition, since the abrasion can be prevented, it is possible to prevent the support points of the movable scroll 2 from being displaced as in the conventional example, and therefore, the sealing property between the scrolls of each scroll is deteriorated and the performance is prevented from being deteriorated. You can do it.

According to the second aspect of the present invention, the annular step portion 56 is formed on the top surface portion of the bearing housing 5, and the annular step portion 56 is cut off from the annular oil groove 54 and the swivel portion 53. Since the thrust bearing member 9 having the oil sump 8 and the thrust receiving surface 52 communicating with the above is fixed, it is not necessary to form the oil sump 8 by processing the bearing housing 5 having a complicated shape. Since the oil sump 8 is formed in the thrust bearing member 9 provided separately from 5, the formation can be facilitated, and the thrust bearing member 9 can be formed easily.
Since it is only necessary to fix the oil reservoir 8 to the annular step portion 56 of the bearing housing 5, the oil sump 8 can be easily formed in the bearing housing 5 and the workability can be improved.

According to the third aspect of the invention, the turning portion 5 in the bearing housing 5 is blocked by the annular oil groove 54.
The oil reservoir 8 communicating with the plurality of grooves 8 extending in the radial direction.
Since the pressure receiving area of the thrust receiving surface 52 is reduced as much as possible, the oil sump 8 can be formed, and the oil supply performance on the radially inner side of the thrust receiving surface 52 is improved. It is possible to improve the lubrication.

Further, the radial outer side of the thrust receiving surface 52 is supplied with oil from the annular oil groove 54, and the radial inner side is supplied with oil from the annular oil groove 54 and the groove 81. Therefore, when the grooves 81 are formed in the radial direction, it is not necessary to make the circumferential pitch of each groove 81 smaller than the orbiting diameter of the movable scroll 2, and therefore, the pressure receiving area of the thrust receiving surface 52 is sufficiently secured. Therefore, the supporting strength can be maintained.

According to the fourth aspect of the invention, the oil sump 8 which is cut off from the annular oil groove 54 and communicates with the swivel portion 53 of the bearing housing 5 is communicated with the swivel portion 53 in the radial direction. A plurality of first grooves 81 extending and the first grooves 81
Since it is formed by the annular second groove 82 communicating with the first groove 81 on the radially outer side, the lubrication on the radially inner side of the thrust receiving surface 52 is performed by the annular oil groove 54 and the oil reservoir 8. And wear can be favorably prevented, and the annular second groove 82 in the oil reservoir 8 is formed further outward in the radial direction than the first groove 81. Therefore, when the fluid machine is stopped, the oil can be stored in the second groove 82, and when the fluid machine is started, the thrust receiving surface 52 can be retained by the oil stored in the second groove 82. Since it is possible to lubricate the inner side in the radial direction in (3), it is possible to prevent poor lubrication at the time of starting the thrust receiving surface 52.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view showing a first embodiment of a scroll type fluid machine of the present invention.

FIG. 2 is a top view of the bearing housing according to the first embodiment as viewed from the thrust receiving surface side.

FIG. 3 is a longitudinal sectional view of a main part in the first embodiment.

FIG. 4 is a cutaway perspective view showing a main part of a bearing housing in the first embodiment.

FIG. 5 is a cutaway perspective view showing a main part of a bearing housing according to a second embodiment.

FIG. 6 is a top view of the bearing housing according to the third embodiment as viewed from the thrust receiving surface side.

FIG. 7 is a cutaway perspective view showing a main part of a bearing housing according to a third embodiment.

FIG. 8 is an explanatory diagram of a conventional scroll type fluid machine.

FIG. 9 is an explanatory view showing a conventional bearing housing.

FIG. 10 is an explanatory view showing another conventional bearing housing.

[Explanation of symbols]

 2 Movable scroll 4 Drive shaft 41 Eccentric shaft portion 42 Main oil supply passage 5 Bearing housing 51 Bearing 52 Thrust receiving surface 53 Swiveling portion 54 Annular oil groove 55 Oil supply passage 56 Annular step portion 8 Oil sump 81 Groove (first groove) 82 Second Groove 9 Thrust bearing member

Claims (4)

[Claims] 1. A swivel part (53) for receiving a bearing (51) of a drive shaft (4) and an eccentric shaft part (41) of the drive shaft (4) and enabling a swivel motion of a movable scroll (2). ) Is provided with a thrust receiving surface (52) for supporting the back surface of the movable scroll (2),
An annular oil groove (54) is provided substantially in the center of the thrust receiving surface (52) in the radial direction, and a main oil supply passage (42) is provided in the bearing housing (5) with one end inside the drive shaft (4).
In a scroll type fluid machine having an oil supply passageway (55) communicating with the annular oil groove (54) and the other end opening to the annular oil groove (54), a radial direction inside the annular oil groove (54) in the thrust receiving surface (52). A scroll type fluid machine characterized in that an oil sump (8) which is cut off from the annular oil groove (54) and communicates with the swivel portion (53) is provided on one side. 2. An annular step portion (56) facing a swirl portion (53) of the bearing housing (5) at a top surface portion of the bearing housing (5) radially inward of the annular oil groove (54).
To form the annular oil groove (5) in the annular step (56).
4. A scroll type fluid machine according to claim 1, wherein a thrust bearing member (9) having an oil sump (8) and a thrust receiving surface (52), which is cut off from 4) and communicates with the swivel portion (53), is fixed. . 3. An oil sump (8), which is cut off from the annular oil groove (54) and communicates with the swirl part (53) of the bearing housing (5), is formed by a plurality of radially extending grooves (81). The scroll type fluid machine according to claim 1 or 2. 4. An oil sump (8) which is cut off from the annular oil groove (54) and communicates with the swirl part (53) of the bearing housing (5) communicates with the swirl part (53) and extends in the radial direction. A plurality of first grooves (81) and an annular second groove (82) communicating with the first grooves (81) radially outward of the first grooves (81). A scroll type fluid machine according to claim 3.