JPH09268983A - Scroll fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil-free scroll fluid machine, make a device smaller as a whole and greatly improve the durability and reliability of the device. SOLUTION: An Oldham's ring is formed of wear resistant material containing 40wt% or so graphite and 15wt% or so fluororesin in polyimide resin as base material. A thrust ring 16 is formed of wear resistant material containing 15wt% or so graphite and 10wt% or so fluororesin in polyimide resin as base material. The Oldham's ring 15 is arranged as another member between a plate cover 11 for a turning scroll 6 and a thrust receiving plate 14. In this way, the Oldham's ring 15 and the thrust ring 16 are improved in wear resistance and the supply of lubricant between each Y-axis key groove 14C and each Y-axis key portion 15C and between slide faces 11C, 16A is eliminated. The thrust load from the turning scroll 6 is received by the thrust ring 16.

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 suitable for use in, for example, an air compressor or a vacuum pump.

[0002]

2. Description of the Related Art Generally, a casing, a fixed scroll integrally provided in the casing, and an orbiting scroll rotatably provided in the casing and defining a plurality of compression chambers between the fixed scroll. A movable joint slidably provided between the casing and the orbiting scroll to prevent rotation of the orbiting scroll, and a thrust load from the orbiting scroll provided between the casing and the orbiting scroll. A scroll type fluid machine provided with a thrust receiver is, for example, Japanese Patent Application No. 6-8556.
Known by No. 8.

In this type of conventional scroll type fluid machine, a drive shaft is rotatably driven from the outside to orbit the orbiting scroll with a fixed eccentric dimension with respect to the fixed scroll, thereby providing it on the outer peripheral side of the fixed scroll. While sucking air (outside air) from the suction port, this air is sequentially compressed in each compression chamber between the wrap portion of the fixed scroll and the wrap portion of the orbiting scroll, and compressed from the discharge port provided at the center of the fixed scroll. It is designed to discharge air to the outside.

In such a conventional technique, an Oldham ring made of one member is slidably disposed between the orbiting scroll and the casing, so that the Oldham ring prevents the orbiting scroll from rotating. And a function as a thrust receiver for receiving the thrust load from the orbiting scroll.

In another conventional technique, a movable joint and a thrust receiver are provided as separate members between a casing and an orbiting scroll, and an oil that rotates integrally with the drive shaft is provided on the drive shaft. A scraping member is provided, and the oil scraping member constantly supplies the lubricating oil accommodated between the casing and the orbiting scroll to the sliding portion of the movable joint, the sliding portion of the thrust receiver, and the like, and to these sliding portions. It is known that the generated sliding resistance is reduced.

[0006]

By the way, in the scroll type fluid machine according to the above-mentioned prior art, an Oldham ring made of one member is slidably disposed between the casing and the orbiting scroll to thereby provide the Oldham ring. In addition, it is configured to have both a function as a movable joint that prevents rotation of the orbiting scroll and a function as a thrust receiver that receives the thrust load from the orbiting scroll.

For this reason, the thrust load from the orbiting scroll acts on the Oldham ring as a large surface pressure. And, in order to make such surface pressure acting on the Oldham ring relatively small, it is necessary to make the entire Oldham ring large.

As a result, the weight of the Oldham ring becomes large, and during the compression operation, the inertial force caused by the sliding movement of the Oldham ring acts on the drive shaft.
As a result, there is no choice but to increase the balance weight and the like provided on the drive shaft, and there is a problem that the size of the entire apparatus increases.

Further, when the Oldham ring is formed in such a large size, thermal expansion of the Oldham ring due to the compression heat from the compression chamber becomes large, and the Oldham ring takes such thermal expansion into consideration. It is necessary to design, high processing accuracy is required when processing the Oldham ring, and noise etc. due to the clearance generated between the Oldham ring and the casing side and between the Oldham ring and the orbiting scroll side at the initial stage of operation. Is likely to occur.

On the other hand, in other prior art, since the thrust receiver and the movable joint are formed as separate members,
When the thrust load becomes large, it is not necessary to increase the size of the movable joint by increasing only the thrust receiver.

However, in such another conventional technique, since the lubricating oil is supplied to the sliding portion of the movable joint and the sliding portion of the orbiting scroll by the oil scraping member, such an oil scraping member is used. Not only is it necessary, but it is necessary to dispose a seal member between the casing and the compression chamber or the like in order to prevent the lubricating oil from entering the compression chambers.

As a result, the number of parts constituting the entire apparatus increases due to the sealing member, the oil scraping member, etc.
There is a problem that the manufacturing cost etc. will rise. Further, since the seal member is formed of a flexible rubber boot or the like, there is a problem that the life of the seal member is apt to be shortened and the durability of the entire device cannot be improved.

The present invention has been made in view of the above-mentioned problems of the prior art. The present invention surely improves the wear resistance and the like of the movable joint and the thrust receiver, realizes oil free, and reduces the size of the entire apparatus. It is an object of the present invention to provide a scroll type fluid machine which can be made more compact, and in which the number of parts and the like can be greatly reduced and durability and reliability can be greatly improved.

[0014]

In order to solve the above-mentioned problems, the present invention provides a casing, a fixed scroll integrally provided in the casing, and a fixed scroll rotatably provided in the casing. Between the orbiting scroll defining a plurality of compression chambers between them, a movable joint slidably provided between the casing and the orbiting scroll to prevent rotation of the orbiting scroll, and the casing and the orbiting scroll. The present invention is applied to a scroll type fluid machine provided with a thrust receiver provided between the thrust receiver and the thrust load from the orbiting scroll.

The feature of the constitution adopted by the invention of claim 1 is that at least one of the movable joint and the thrust receiver is made of a polyimide resin material as a base material, graphite and fluorine resin. It is characterized by being formed of an abrasion resistant resin material mixed with a material.

With this structure, at least one of the movable joint and the thrust receiver is provided with a wear-resistant resin obtained by mixing graphite and a fluorine-based resin material with a polyimide resin material as a base material on the sliding portion side. It can be formed of a material, the abrasion resistance of these sliding parts can be easily improved in sliding characteristics, and lubrication oil supply to the sliding parts can be eliminated. .

According to the second aspect of the invention, the polyimide resin material as the base material of the abrasion resistant material is mixed with about 40% by mass of graphite and about 15% by mass of a fluorine resin material. Are formed.

As a result, the abrasion resistance of the polyimide resin material as the base material is approximately 40% by mass when mixed with the polyimide resin material.
Can be easily improved from the graphite and the fluororesin material of about 15% by mass.

Further, in the invention according to claim 3, the wear resistant material is a polyimide resin material as a base material, and the wear resistance material is approximately 15
It is formed by mixing mass% graphite and approximately 10 mass% fluorine-based resin material.

As a result, similarly to the second aspect of the present invention, it is possible to easily improve the amount of graphite and the fluorine-based resin material of about 15% by mass mixed with the polyimide resin material as the base material. You can

Furthermore, in the invention according to claim 4, either one of the movable joint and the thrust receiver is
The polyimide resin material as the base material is formed of a wear-resistant resin material in which approximately 40% by mass of graphite and approximately 15% by mass of a fluorine-based resin material are mixed, and the other member is substantially the same as the polyimide resin material as the base material. 15% by mass graphite and approximately 10
It is formed of an abrasion-resistant resin material mixed with a mass% of a fluorine-based resin material.

As a result, the wear resistance between the movable joint and the thrust receiver can be easily improved as in the invention according to claim 2 or 3.

On the other hand, in the invention according to a fifth aspect, the thrust receiver is formed by a ring body having a U-shaped or H-shaped cross section so as to elastically deform in response to a thrust load from the orbiting scroll. It has been formed.

As a result, an elastic opposing force against the thrust load from the orbiting scroll can be generated in the thrust receiver, and the orbiting scroll can be constantly pressed to the fixed scroll side by utilizing the elastic force of the thrust receiver. it can. As a result, rattling can be prevented from occurring between the orbiting scroll and the fixed scroll, and the degree of airtightness in each compression chamber formed between the fixed scroll and the orbiting scroll can be increased.

According to the sixth aspect of the invention, a backup ring for elastically pressing the thrust receiver toward the orbiting scroll is provided between the casing and the thrust receiver.

As a result, an elastic opposing force against the thrust load from the orbiting scroll can be generated in the backup ring, and the orbiting scroll is moved to the fixed scroll side via the thrust receiver by utilizing the elastic force of this backup ring. It can be pressed at all times. As a result, the degree of airtightness in each compression chamber formed between the fixed scroll and the orbiting scroll can be increased similarly to the invention described in claim 5. Also, the overall shape of the thrust receiver can be simplified.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a case where a scroll type fluid machine according to an embodiment of the present invention is used for a scroll type air compressor will be described as an example.

Here, a first embodiment of the present invention will be described with reference to FIGS.

In the drawing, reference numeral 1 denotes a stepped cylindrical casing constituting the main body of the scroll type air compressor, and the casing 1 has a bottomed cylindrical casing main body 1A.
And a small-diameter cylindrical bearing portion 1B opened in the central portion of the casing body 1 and an annular abutment portion 1C extending radially outward from the opening end of the casing body 1A. There is.

Reference numeral 2 denotes a fixed scroll integrally provided on the tip end side of the casing 1. The fixed scroll 2 and a substantially disc-shaped end plate 2A arranged so as to coincide with the axis of a drive shaft 3 described later. The mounting flange portion 2B protruding from the outer edge side of the end plate 2A and having the outer peripheral side fixed to the abutting portion 1C of the casing 1 via a bolt or the like, and the end side extending axially from the front surface side of the end plate 2A and the center side being wound. A spiral wrap portion 2C having a start end and an outer peripheral end serving as a winding end, and a plurality of heat dissipating fins 2D, 2D, ... Standing in parallel on the back surface side of the end plate 2A, are roughly configured. Further, the mounting flange 2B is formed with an annular recessed groove 2E in which an end face 2B1 on the side of the orbiting scroll 6 is fitted with a face seal 17 described later.

Reference numeral 3 denotes a drive shaft rotatably supported by a bearing portion 1B of the casing 1 via a bearing 4, and the drive shaft 3
The front end side of the crank extends to the inside of the casing 1 to form the crank 3A, and the axis of the crank 3A is eccentric to the axis of the drive shaft 3 by a predetermined dimension. The drive shaft 3 is connected to a drive source (not shown) on the base end side protruding outside the casing 1, and is rotationally driven by the drive source, whereby the crank 3
The orbiting scroll 6 to be described later is orbitally moved via A.

Reference numeral 5 denotes a balance weight, which is fixed to the base end side of the crank 3A to balance the rotation of the drive shaft 3 with respect to the orbiting movement of the orbiting scroll 6.

Reference numeral 6 denotes an orbiting scroll which is disposed so as to be able to orbit in the casing 1 so as to face the fixed scroll 2. The orbiting scroll 6 includes an orbiting scroll body 7 and a rear side of the orbiting scroll body 7 which will be described later. Is integrally formed with the plate-shaped cover 11 attached to the.

Reference numeral 7 denotes an orbiting scroll body. The orbiting scroll body 7 is provided with a disk-shaped end plate 7A and is erected on the surface of the end plate 7A. The center side of the end plate 7A serves as the winding start end and the outer peripheral side The spiral wrap portion 7B which is the end of the winding, and the radiation fins 7 which are erected on the back side of the end plate 7A.
C.

Here, the wrap portion 7B of the orbiting scroll main body 7 is disposed so as to overlap with the wrap portion 2C of the fixed scroll 2 by a predetermined angle and overlap with each other.
A plurality of compression chambers 8, 8, ... Are formed between C and 7B.

During operation of the scroll air compressor, the orbiting scroll 6 orbits while sucking air into the compression chamber 8 on the outer peripheral side from the suction port 9 provided on the outer peripheral side of the fixed scroll 2. In the meantime, the respective compression chambers 8 are sequentially compressed, and finally from the compression chamber 8 on the center side to the discharge port 10 provided at the center of the fixed scroll 2 to a discharge pipe 20 described later.
Compressed air is discharged to the outside via the.

Reference numeral 11 denotes a plate-like cover provided on the back side of the orbiting scroll body 7, and the plate-like cover 11 is shown in FIG.
As shown in FIG. 7, the cover body 11A is formed in the shape of a stepped disc having the same diameter as the end plate 7A of the orbiting scroll body 7, and the boss portion 11B is formed at the center of the cover body 11A so as to project in the axial direction. And two elongated X-axis key grooves (not shown) formed on the cover body 11A on both the left and right sides of the boss portion 11B.

The plate-like cover 11 is the cover body 1
1A is integrally attached to the orbiting scroll main body 7 via bolts (not shown) or the like so as to abut the tip surface of each heat radiation fin 7C, and the boss portion 11B is attached to the crank 3A of the drive shaft 3 to the orbit bearing 12. It is rotatably attached via.

Here, the plate-like cover 11 has an annular sliding surface 11C on the outer peripheral side of the cover body 11A, and the sliding surface 11C contacts a sliding surface 16A of a thrust ring 16 described later via a face seal 17. The thrust force (hereinafter referred to as the thrust load from the orbiting scroll 6) generated in each compression chamber 8 is received between the sliding surface 16A and the sliding surface 16A.

Further, the plate-like cover 11 defines cooling air passages 13, 13, ... Between the orbiting scroll body 7 and the rear side of the end plate 7A via the radiation fins 7C, and is formed in each compression chamber 8. The high-temperature compression heat is efficiently radiated from the back surface side of the end plate 7A to the cooling air passage 13 side through the radiation fins 7C, so that the cooling efficiency in each compression chamber 8 is increased.

Reference numeral 14 denotes a casing body 1A of the casing 1.
With the thrust receiving plate provided on the side, the thrust receiving plate 14
Is a short cylindrical thrust receiving portion 14A whose outer peripheral side is fixed to the inner peripheral surface of the casing body 1A, and the thrust receiving portion 14A.
It is composed of a disk-shaped guide portion 14B which projects radially inward from the inner peripheral surface of A and has a through hole 14B1 formed therein. The guide hole 14B has a through hole 1
Two Y-axis keyways 14C, 14C are formed on the 4B1 side.

Reference numeral 15 is a plate-like cover 11 and a thrust receiving plate 14.
An Oldham ring as a movable joint slidably disposed between the Oldham ring and the Oldham ring is shown in FIGS. 1 to 4, and the Oldham ring 15 is injection molded from a wear-resistant resin material having self-lubricity. It is formed into a stepped disc shape by using the above means.

Here, the abrasion-resistant resin material is made up of about 40% by mass of polyimide resin material of about 45% by mass as a base material.
It is preferable that the graphite is mixed with approximately 15% by mass of a fluorine-based resin material. In addition, the Oldham ring 15 has a polyimide resin material of about 75% by mass as a base material and a polyimide resin material of about 15% by mass.
You may form from the abrasion-resistant resin material which mixed the graphite of mass%, and the fluororesin material of about 10 mass%. In addition, it is preferable to use polytetrafluoroethylene (PTFE) as the fluororesin material.

The Oldham ring 15 includes an annular ring portion 15A and a plate-like cover 11 of the ring portion 15A.
Two X-axis key portions 15B and 15B projectingly formed from the side end surface at positions corresponding to the respective X-axis key grooves, and the ring portion 1.
From each thrust receiving plate 14 side end face of 5A, each Y-axis key groove 14C
Two Y-axis key portions 15 protrudingly formed at positions corresponding to
It is composed of C and 15C.

The Oldham ring 15 has a key portion 1
5B and 15C are slidably displaced along the Y-axis keyways 14C and the like. As a result, the Oldham ring 15 is relatively displaced in the Y-axis direction with respect to the thrust receiving plate 14, and the plate-shaped cover 11 is relatively displaced in the X-axis direction with respect to the Oldham ring 15. The rotation of the orbiting scroll 6 is prevented, and the orbiting scroll 6 is given a circular motion (orbital motion) having a turning radius of a predetermined dimension.

Reference numeral 16 is a plate-like cover 11 and a thrust receiving plate 14.
1 and 2 by using a means such as injection molding made of a wear-resistant resin material like the Oldham ring 15. It is formed as shown in FIG.

Here, the abrasion resistant resin material is approximately 75
It is preferable to use, as a base material, a polyimide resin material of about mass% and an abrasion resistant resin material in which about 15 mass% of graphite and about 10 mass% of a fluorine-based resin material are mixed with the polyimide resin material. Also, the Oldham ring 1
5 is a polyimide resin material of about 45 mass% as a base material,
The polyimide resin material may be formed by mixing approximately 40% by mass of graphite and approximately 15% by mass of a fluorine-based resin material. In addition, it is preferable to use polytetrafluoroethylene (PTFE) as the fluororesin material.

The thrust ring 16 has an outer peripheral surface fixed to the inner peripheral surface of the casing body 1 of the casing 1, and one end surface of the thrust receiving portion 14A (thrust receiving plate 14) located on the orbiting scroll 6 side. Is stuck to.

Here, the thrust ring 16 has a sliding surface 1 on the other side end surface with respect to the sliding surface 11C of the plate-like cover 11.
6A. The thrust ring 16 applies the thrust load from the orbiting scroll 6 to the sliding surface 11C,
It is configured to be received together with the thrust receiving portion 14A via 16A, and to prevent such thrust load from directly acting on the Oldham ring 15.

Reference numeral 17 denotes a face seal mounted in the concave groove 2E of the fixed scroll 2. The face seal 17 is
The elastic ring 17A is made of a resin material or the like and has a circular cross section, and the seal ring 17B is made of a resin material or the like and has a substantially rectangular cross section. The seal ring 17B may be formed of the same abrasion resistant resin material as the Oldham ring 15 and the thrust ring 16.

Here, the elastic ring 17A is disposed on the back side of the recessed groove 2E in a state of being elastically deformed, and the seal ring 17B is disposed on the front side (opening side) of the recessed groove 2E. . The face seal 17 is the elastic ring 1.
By making elastic contact of the seal ring 17B with the surface of the orbiting scroll 6 on the outer peripheral side of the end plate 7A (sliding contact) using the elastic force of 7A, the sliding surface 1 of the plate-shaped cover 11
1C is constantly pressed against the sliding surface 16A of the thrust ring 16 and the surface of the end plate 7A is the end surface 2 of the fixed scroll 2.
It is constructed so as to prevent direct sliding contact with B1.

The face seal 17 also seals between the end surface 2B1 of the fixed scroll 2 and the surface of the end plate 7A via a seal ring 17B to enhance the compression efficiency in each compression chamber 8. .

Reference numeral 18 denotes each radiation fin 2 of the fixed scroll 2.
D shows a cover plate fixed to the front end surface,
Is the end plate 2 of the fixed scroll 2 through each heat radiation fin 2D.
A plurality of cooling air passages 19, 19, ... Are defined between the rear surface A and the cooling air passages 19 from the outside to flow in the respective cooling air passages 19. The compression heat and the like can be efficiently radiated to the outside through each radiation fin 2D. A through hole 18A is formed in the center of the cover plate 18, one end side of the discharge pipe 20 is connected to the discharge port 10, and the other end side is the through hole 18A.
It opens to the outside through.

The scroll type air compressor according to the present embodiment has the above-mentioned construction, and its compressing operation will be described below.

First, when the drive shaft 3 is rotated by the drive source, the orbiting scroll 6 is orbitally driven, whereby the wrap portion 2C of the fixed scroll 2 and the orbiting scroll body 7 are rotated.
The compression chambers 8,8, ... As a result, the outside air sucked from the suction port 9 of the fixed scroll 2 is sequentially compressed in each compression chamber 8,
This compressed air is discharged from the discharge port 10 of the fixed scroll 2 through the discharge pipe 20 to an external air tank or the like.

During the orbiting motion of the orbiting scroll 6 as described above, the Oldham ring 15 has the key portions 15B, 1
5C slides along the X-axis key groove of the plate cover 11 and the Y-axis key groove 14C of the thrust receiving plate 14, thereby preventing the orbiting scroll 7 from rotating.

Here, the Oldham ring 15 is a wear-resistant resin material obtained by mixing approximately 40% by mass of graphite and approximately 15% by mass of a fluorinated resin material in a polyimide resin material of approximately 45% by mass as a base material. Since it is formed by, it is possible to significantly reduce the sliding resistance generated between the respective key portions 15B and 15C and the respective Y-axis key grooves 14C.

The plate-like cover 11 is attached to the face seal 1
Since it is in contact with the sliding surface 16A of the thrust ring 16 via 7, the thrust load from the orbiting scroll 6 generated during the compression operation can be received between the sliding surfaces 11C and 16A. It is possible to reliably prevent the thrust load from acting as a large surface pressure and directly acting on the Oldham ring 15.

Here, the thrust ring 16 is a wear-resistant resin material obtained by mixing approximately 15% by mass of graphite and approximately 10% by mass of a fluorine-based resin material in a polyimide resin material of approximately 75% by mass as a base material. Therefore, it is possible to significantly reduce the sliding resistance generated on the sliding surface 16A.

Therefore, in this embodiment, the Oldham ring 15 is used.
The wear resistance and sliding characteristics between the thrust ring 16 and the thrust ring 16 can be surely improved, and the sliding surface 11 and the key portions 15B and 15C and the key grooves 14C of the thrust receiving plate 14 and the like can be reliably improved.
It is not necessary to supply lubricating oil or the like between C and 16A, and the scroll compressor can be made oil-free.

Further, as described in the prior art, it is possible to eliminate the oil scraping member, the sealing member for blocking the invasion of the lubricating oil into the compression chamber 8 and the like, thus reducing the number of parts constituting the entire apparatus. Therefore, it is possible to surely reduce the manufacturing cost and the like of the entire apparatus, and it is possible to significantly improve the durability and reliability of the apparatus.

Moreover, since the Oldham ring 15 and the thrust ring 16 are formed as separate members, in order to increase the mechanical strength of the Oldham ring 15 against the thrust load from the orbiting scroll 6 as described in the prior art, It is possible to eliminate the need to form the Oldham ring 15 by increasing the wall thickness and the like, reduce the weight of the Oldham ring 15, and increase the inertial force due to the sliding displacement of the Oldham ring 15 on the drive shaft 3. It is possible to effectively prevent the above action.

As a result, it is possible to eliminate the need to form the balance weight 5 and the like together with the Oldham Oldham ring 15 in a large size, and it is possible to surely reduce the size and weight of the entire apparatus. Further, the thermal expansion of the Oldham ring 15 as a whole due to the compression heat or the like from each compression chamber 8 can be made small, whereby each of the key portions 15B and 15C and each Y portion.
The clearance between the shaft key groove 14C and the like can be reduced, and vibration, noise, and the like that occur during compression operation can be significantly reduced.

Further, the processing accuracy required for the Oldham ring 15 can be lowered, and the manufacturing cost of the Oldham ring 15 and the number of processing steps can be surely improved. Moreover, the entire thrust ring 16 can be formed to be large, the area of the sliding surface 16A can be increased, the surface pressure from the orbiting scroll 6 can be relatively reduced, and the wear resistance of the thrust ring 16 can be improved. It can be surely improved.

Next, FIG. 5 shows a second embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. To do. However, the feature of this embodiment is that the thrust ring 31 is formed to have a substantially U-shaped cross section so that the thrust ring 31 is elastically deformed according to the thrust load from the orbiting scroll 6. .

Here, the thrust ring 31 is made of a wear-resistant material obtained by mixing graphite and a polyimide resin material into a polyimide resin material, which is a base material, in substantially the same manner as the thrust ring 16 described in the first embodiment. Formed from
Although having a sliding surface 31A, the thrust ring 3
1, an annular groove 31B having a U-shaped cross section is formed on the inner peripheral side thereof,
By slightly elastically deforming with the thrust load from the orbiting scroll 6, an elastic opposing force (repulsive force) against this thrust load is generated.

The thrust ring 31 generates a plate-like sliding surface 31A by generating an elastic force corresponding to the thrust force generated in each compression chamber 8 during the steady operation of the scroll type air compressor. Sliding surface 1 of cover 11
1C is elastically brought into sliding contact (contact).

Further, the thrust ring 31 prevents the elastic pressing force toward the orbiting scroll 6 side from becoming excessive, and cooperates with the face seal 17 on the fixed scroll 2 side so that the end plate 7A of the orbiting scroll 6 is formed. Preventing strong frictional contact with the end surface 2B1 of the fixed scroll 2,
It is possible to prevent galling and the like between the end plate 7A and the end surface 2B1.

Thus, in this embodiment having such a structure, the same effect as that of the first embodiment can be obtained. In particular, however, in this embodiment, the cross section of the thrust ring 31 is substantially U-shaped. By forming into a shape, the sliding surface 31A
Can be brought into contact with the sliding surface 11C of the plate-like cover 11 with a large elastic force.

As a result, the sliding surface 3 of the thrust ring 31
Even when 1A is worn or the like, it is possible to effectively prevent a gap from being formed in the thrust direction between the sliding surface 31A and the sliding surface 11C of the orbiting scroll 6, and the orbiting scroll 6 with respect to the fixed scroll 2 can be effectively prevented. Rattling can be effectively prevented, and it is possible to prevent the sealing degree in the compression chamber 8 from being lowered due to such rattling, and it is possible to maintain the compression performance and the like of the scroll type compressor for a long period of time. it can.

Next, FIG. 6 shows a third embodiment of the present invention. In this embodiment, the same components as those of the second embodiment are designated by the same reference numerals and the description thereof will be omitted. To do. However, the feature of this embodiment is that the thrust ring 41 is formed to have an H-shaped cross section so that the thrust ring 41 is elastically deformed according to the thrust load from the orbiting scroll 6. .

Here, although the thrust ring 41 is formed in substantially the same manner as the thrust ring 31 described in the second embodiment and has the sliding surface 41A and the annular groove 41B, the thrust ring 41 is the same. 31 has a cross section U on the outer peripheral side thereof.
The annular groove 41C is formed and slightly elastically deformed by the thrust load from the orbiting scroll 6, so that an elastic opposing force (repulsive force) against the thrust load is generated.

Thus, in this embodiment having the above-mentioned structure, it is possible to obtain the same effects as the second embodiment.

Next, FIG. 7 shows a fourth embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. To do. However, the feature of this embodiment is that the thrust receiving portion 1 of the thrust receiving plate 14 in which the annular concave groove 51 is located on the side of the orbiting scroll 6 is used.
4A is formed on the end face, and the backup ring 52 and the thrust ring 53 are mounted in the recessed groove 51, whereby the thrust ring 53 is fixed to the backup ring 5.
It is configured to be pressed to the side of the orbiting scroll 6 via 2.

Here, the backup ring 52 is
Similar to the elastic ring 17A of the face seal 17 described in the first embodiment, the face seal 17 is formed from an elastic resin material or the like so as to have an annular cross section, and is elastically deformed to the inner side in the concave groove 51. It is arranged in a closed state. Further, the thrust ring 53 is formed in the same manner as the thrust ring 16 described in the first embodiment, and is disposed on the near side in the concave groove 51 via the backup ring 52.

Then, the backup ring 52 generates an elastic force that opposes the thrust force generated in each compression chamber 8 during the steady operation of the scroll type air compressor, thereby causing the sliding surface of the thrust ring 53 to move. 53A elastically slidably contacts (abuts) the sliding surface 11C of the plate-like cover 11.
Let me.

Thus, also in this embodiment having the above-mentioned structure, the thrust ring 5 is provided by the backup ring 52.
It is possible to generate an elastic pressing force toward the orbiting scroll 6 side in 3 and to obtain substantially the same action and effect as in the second and third embodiments. In the ring 53, the annular groove 32B (41B,
41C) can be eliminated, the workability of the thrust ring 53 can be improved, and the manufacturing cost can be reduced.

In each of the above embodiments, the Oldham ring 15 and the thrust ring 16 are described as being formed of different wear resistant materials, but instead, both of them are about 45 mass% of polyimide. It may be formed of an abrasion resistant resin material in which a resin material is mixed with approximately 40% by mass of graphite and approximately 15% by mass of a fluororesin material. Alternatively, both may be formed of an abrasion resistant resin material in which approximately 15% by mass of graphite resin and approximately 10% by mass of fluorine resin material are mixed in approximately 75% by mass of polyimide resin material.

Further, in each of the above-mentioned embodiments, the Oldham ring 15 and the thrust ring 16 (31, 41, 5) as a whole.
3) Although the whole is described as being formed of the wear resistant resin material, the present invention is not limited to this, and the Oldham ring 15 is used.
Surface side and thrust ring 16 (31, 41, 5
Only the surface side of 3) may be formed of such an abrasion resistant resin material.

The present invention is not limited to the mixing ratio described in each of the above embodiments, but the mixing ratio of graphite and fluorine resin to the polyimide resin material as the base material is
For example, it may be changed within the range of several mass%.

Further, in each of the above-mentioned embodiments, the scroll type air compressor has been described as an example, but the present invention is not limited to this, and can be applied to a compressor for compressing a gas other than air,
It can also be applied to a vacuum pump or the like.

[0082]

As described in detail above, according to the present invention, as described in claim 1, at least one of the movable joint and the thrust receiver is made of a polyimide resin material as a base material, graphite and fluorine. Since it is formed of a wear-resistant resin material mixed with a system resin material, it is possible to eliminate the need to supply lubricating oil or the like to the sliding portion side of the movable joint or the sliding portion side of the thrust receiver. Oil-free can be realized. Further, as described in the prior art, it is possible to eliminate the oil scraping member, the seal member for blocking the intrusion of the lubricating oil into the compression chamber, reduce the number of parts, and reduce the manufacturing cost of the entire device. It is possible to surely reduce it, and it is possible to greatly improve the durability and reliability of the device.

Further, by forming the movable joint and the thrust receiver as separate members, it is not necessary to upsize the movable joint in accordance with the thrust load from the orbiting scroll, and the overall size and weight of the device can be reduced. It can be achieved reliably. Further, the thermal expansion of the entire movable joint due to the compression heat from each compression chamber can be reduced, the clearance between the movable joint and the casing side and between the movable joint and the orbiting scroll side can be reduced, and during compression operation. The generated vibration, noise, etc. can be significantly reduced.

On the other hand, in the invention described in claim 2, the wear resistance of the movable joint and the thrust receiver can be easily improved, and the sliding portion side of the movable joint and the sliding portion side of the thrust receiver can be easily improved. It is not necessary to supply lubricating oil or the like, and the scroll compressor can be made oil-free.

Further, in the invention described in claim 3, similarly to the invention described in claim 2, the supply of lubricating oil or the like to the sliding portion side of the movable joint and the sliding portion side of the thrust receiver can be made unnecessary. ,
The scroll compressor can be made oil-free.

Furthermore, in the invention described in claim 4,
Similarly to the invention described in claim 2, it is possible to eliminate the need to supply lubricating oil or the like to the sliding portion side of the movable joint and the sliding portion side of the thrust receiver, and to realize the oil free of the scroll compressor. You can

According to the fifth aspect of the present invention, it is possible to prevent rattling between the orbiting scroll and the fixed scroll even when the thrust bearing is worn, and this reduces the degree of airtightness in each compression chamber. Can be prevented, and the compression performance of the scroll type fluid machine can be compensated for a long period of time.

Further, in the invention described in claim 6, the overall shape of the thrust receiver can be simplified, the workability of the thrust receiver can be improved, and the manufacturing cost can be reduced.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a scroll type air compressor according to a first embodiment of the present invention.

FIG. 2 is an enlarged view of essential parts showing an Oldham ring, a thrust ring and the like in FIG.

3 is an enlarged front view showing an Oldham ring in FIG. 1. FIG.

FIG. 4 is a sectional view taken along the line VI-VI in FIG.

FIG. 5 is a sectional view similar to FIG. 2, showing a scroll air compressor according to a second embodiment of the present invention.

FIG. 6 is an enlarged sectional view similar to FIG. 2, showing a scroll air compressor according to a third embodiment of the present invention.

FIG. 7 is an enlarged sectional view similar to FIG. 2, showing a scroll air compressor according to a fourth embodiment of the present invention.

[Explanation of symbols]

1 casing 2 fixed scroll 6 orbiting scroll 8 compression chamber 15 Oldham ring (movable joint) 16, 31, 41, 53 thrust ring (thrust receiver) 52 backup ring

Claims (6)

[Claims] 1. A casing, a fixed scroll integrally provided in the casing, a swivel scroll provided in the casing so as to be swivelable and defining a plurality of compression chambers between the fixed scroll, and A movable joint that is slidably provided between the casing and the orbiting scroll to prevent the orbiting scroll from rotating, and a thrust that is provided between the casing and the orbiting scroll and receives a thrust load from the orbiting scroll. In a scroll fluid machine including a receiver, at least one of the movable joint and the thrust receiver is a wear-resistant resin material obtained by mixing graphite and a fluorine-based resin material into a polyimide resin material serving as a base material. A scroll-type fluid machine characterized by being formed by. 2. The wear-resistant material is formed by mixing a polyimide resin material as a base material with approximately 40% by mass of graphite and approximately 15% by mass of a fluorine-based resin material. The scroll-type fluid machine described. 3. The wear-resistant material is formed by mixing a polyimide resin material as a base material with approximately 15% by mass of graphite and approximately 10% by mass of a fluorine-based resin material. The scroll-type fluid machine described. 4. One of the movable joint and the thrust receiver is made of a polyimide resin material serving as a base material.
It is made of a wear-resistant resin material in which 0% by mass of graphite and about 15% by mass of a fluorine-based resin material are mixed, and the other member is a polyimide resin material as a base material, and about 15% by mass of graphite and about 10% by mass. % Of a fluorine-based resin material, the scroll-type fluid machine according to claim 1, which is formed of a wear-resistant resin material. 5. The thrust receiver is formed by a ring body having a U-shaped or H-shaped cross section so as to elastically deform in response to a thrust load from the orbiting scroll. , 3 or 4, scroll type fluid machinery. 6. The scroll according to claim 1, 2, 3 or 4, wherein a backup ring that elastically presses the thrust receiver toward the orbiting scroll is provided between the casing and the thrust receiver. Fluid machinery.