JPH1047264A - Scroll fluid machinery - Google Patents

Abstract

PROBLEM TO BE SOLVED: To bear the thrust load from a revolving scroll and stabilize the revolving operation of the revolving scroll over a long period of time. SOLUTION: A slider 16 is disposed between a casing 1 and the back of a a revolving scroll 7 in such a manner as to slide, a slider 16 is slid and displaced in the direction of a Y-axis by each Y-axis guide 15 of the casing 1 side, and the revolving scroll 7 is slid and displaced to the slider 16 in the direction of an X-axis by each X-axis guide 14 of the revolving scroll 7 side. Each sphere 17 is accommodated in each through hole 16C of the slider 16, and each sphere 17 is rolled between the support plates 19 respectively provided on each support 12 of the casing 1 side and the revolving scroll 7.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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 provided integrally with the casing, a drive shaft having a base end rotatably supported by the casing and a distal end serving as a crank, and orbiting about the crank of the drive shaft 2. Description of the Related Art There is known a scroll-type fluid machine that includes an orbiting scroll that is provided to define a plurality of compression chambers between the orbiting scroll and a fixed scroll, and a rotation preventing mechanism that prevents the orbiting scroll from rotating.

In this type of scroll fluid machine according to the related art, the orbiting scroll is rotationally driven from the outside with a fixed eccentric dimension relative to the fixed scroll by driving the drive shaft from the outside, so that the orbiting scroll is provided on the outer peripheral side of the fixed scroll. While sucking fluid (e.g., air) from the suction port, the fluid is sequentially compressed in each compression chamber between the wrap portion of the fixed scroll and the wrap portion of the orbiting scroll, and is discharged from the discharge port provided at the center of the fixed scroll. The compressed fluid is discharged to the outside.

Here, as a first prior art, for example, in an oilless scroll type fluid machine described in Japanese Patent Application Laid-Open No. 2-2777984, a plurality of auxiliary cranks are provided in order to prevent the orbiting scroll from rotating. Is known. That is, a plurality of auxiliary cranks are provided between the casing and the rear side of the orbiting scroll and on the outer peripheral side of the orbiting bearing provided on the orbiting scroll, thereby preventing the orbiting scroll from rotating.

As a second prior art, for example, US Pat. No. 3,994,635 discloses an Oldham coupling which prevents the orbiting scroll from rotating. And in the case of a rotation prevention mechanism by this kind of Oldham coupling,
In order to maintain the lubricating property of the Oldham coupling, the lubricating oil is always supplied to the sliding portion of the Oldham coupling.

Further, as a rotation preventing mechanism according to the third prior art, for example, Japanese Patent Application Laid-Open No. 58-135302 or Japanese Patent Application Laid-Open No. 60-198301 discloses a number of spherical bodies and the same number of guide holes. There is disclosed a ball-coupling type ball comprising two ring-shaped plates, wherein the sphere has a function of preventing rotation of the orbiting scroll and a function of a thrust bearing against a thrust load of the orbiting scroll.

Further, as a fourth prior art, for example, in Japanese Patent Application Laid-Open No. 55-155916, a plurality of grooves serving as guides are provided on the casing and on the back side of the orbiting scroll, and The sphere is accommodated between the groove on the scroll side.

[0008]

By the way, in the scroll type fluid machines according to the above-mentioned prior arts, the compression chamber formed between the fixed scroll and the orbiting scroll during operation when used as a scroll type compressor, for example. Becomes high pressure, the orbiting scroll is pressed in the thrust direction, and the following problems occur.

That is, in the first prior art, the thrust direction pressing force is received by a plurality of combined angular bearings that support each auxiliary crank. Therefore, the structure of the auxiliary crank and the like is complicated by the angular bearing. In addition, the number of parts is increased and the assemblability is deteriorated, and the entire apparatus is enlarged. In addition, it is necessary to match the eccentric dimensions of each auxiliary crank and the drive shaft, and high-precision machining is required.

On the other hand, in the second prior art, the thrust force from the orbiting scroll in the thrust direction directly acts on both surfaces of the Oldham coupling for preventing the rotation of the orbiting scroll, so that the Oldham coupling wears when sliding. Therefore, there is a problem that the performance of the compression operation is deteriorated.

[0011] Further, although the rotation preventing mechanism using this kind of Oldham coupling has the advantages of a relatively simple structure and relatively easy design and manufacture, such a rotation preventing mechanism has the advantage of using an Oldham coupling. The lubricating oil must always be supplied to the sliding portion of the cylinder, and can be applied to a lubricating scroll type fluid machine. However, there is a problem that it is difficult to apply to a non-lubricating type.

Further, in a rotation preventing mechanism using a ball coupling method as a third prior art, it is difficult to accurately adjust a radial gap size, and it is also necessary to block noise generated from a sphere. It is difficult to make the thickness of the ring-shaped plate sufficiently large, so that there is a problem that the ring-shaped plate is worn or deformed.

Further, in the fourth prior art, the thrust direction pressing force is received by the respective grooves provided on the casing side and the orbiting scroll side via the spherical body, so that the casing and the orbiting scroll have strength and wear resistance. And the selection of materials is difficult.

The present invention has been made in view of the above-described problems of the prior art, and the present invention can reliably receive a load in the thrust direction from the orbiting scroll, and can stabilize the orbiting operation of the orbiting scroll. Another object of the present invention is to provide a scroll-type fluid machine that can reliably improve durability and life even when applied to a non-lubricating type, and can increase reliability.

[0015]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a casing, a fixed scroll integrally provided with the casing, a base end rotatably supported by the casing and a tip end rotatably supported by the casing. A orbiting scroll that defines a plurality of compression chambers between the drive shaft that has become a crank, the fixed scroll that is rotatably provided on the crank of the drive shaft, and a rotation prevention mechanism that prevents rotation of the orbiting scroll. For a scroll type fluid machine.

The first aspect of the present invention is characterized in that it is slidably disposed between the casing and the back side of the orbiting scroll, and is spaced apart in the circumferential direction of the orbiting scroll in the thrust direction. A plurality of through holes extending through the slider, and a casing side and a back side of the orbiting scroll inserted into each through hole of the slider to receive a thrust load from the orbiting scroll. A rolling element that comes into contact with the rolling element, and a first and a second wear-resistant portion are provided on the casing side and the rear side of the orbiting scroll at portions where the rolling elements contact each other. And that

According to this structure, the load in the thrust direction from the orbiting scroll can be reliably received between each rolling element and each wear-resistant portion, and the load directly acts on the slider. Thus, the sliding resistance applied to the slider between the casing and the orbiting scroll can be reliably reduced. In addition, the first and second wear-resistant portions can reliably prevent wear on the casing side abutting against each rolling element and the rear side of the orbiting scroll, and smoothly roll each rolling element for a long period of time. Therefore, the slidability of the slider can be greatly improved.

In the invention described in claim 2, fitting recesses into which the first and second wear-resistant portions are inserted are formed on the casing side and the rear side of the orbiting scroll, respectively. An elastic member is provided between the fitting concave portion and each of the wear resistant portions to elastically support the wear resistant portion in each of the fitting concave portions.

As a result, each wear-resistant portion can be detachably provided at the contact portion of each rolling element rolling between the casing side and the back side of the orbiting scroll, and each wear-resistant portion is provided with a corresponding one of the wear-resistant portions. The displacement in the fitting recess can be prevented by the elastic member, and the load in the thrust direction from the orbiting scroll can be reliably received.

Further, in the invention described in claim 3, at least one of the first and second wear-resistant portions has a ring corresponding to a rolling locus of each of the rolling elements. A ring-shaped groove having a diameter is formed.

With this configuration, the first and second wear-resistant portions provided on the casing side and the orbiting scroll side and each rolling element can always be kept in a spherical contact state, and the contact surface pressure between them can be maintained. And a large thrust load can be reliably received.

Further, in the invention described in claim 4, at least one of the rolling elements and the wear-resistant portions is formed of partially stabilized zirconia.

Further, in the invention described in claim 5, at least one of the rolling elements and the wear-resistant portions is formed of a hard metal material having a Rockwell C hardness of 55 or more. Each rolling element is lubricated with a lubricant.

[0024]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

FIGS. 1 to 3 show a first embodiment in which the scroll type fluid machine of the present invention is applied to a scroll type air compressor.

In FIG. 1, reference numeral 1 denotes a stepped cylindrical casing. The casing 1 includes a bearing 1A into which one end (base end) of a drive shaft 3 described later is inserted, and a casing 1A of the bearing 1A. It is roughly composed of a flange portion 1B integrally formed on the other end side, and a cylindrical large-diameter portion 1C extending from the outer peripheral side of the flange portion 1B toward the other side. As shown in FIG. 2, support members 12 described later are formed integrally or separately on the flange portion 1 </ b> B of the casing 1.

Reference numeral 2 denotes a fixed scroll fixed to the distal end of the large diameter portion 1C of the casing 1.
Is such that the center coincides with the axis O1-O1 of the drive shaft 3.
A mirror plate 2A disposed at the center, a spiral wrap portion 2B standing upright from the surface of the mirror plate 2A and having a winding start end on the center side and a winding end end on the outer peripheral side, and a wrap portion 2B having a diameter The mounting portion 2 is integrally formed on the outer peripheral side of the end plate 2A so as to surround from the outer side in the direction, and is fixed to the large diameter portion 1C of the casing 1.
C.

Reference numeral 3 denotes a bearing 4 on the bearing 1A of the casing 1.
5 shows a drive shaft rotatably supported via 5, and the distal end side of the drive shaft 3 extends into the large diameter portion 1 </ b> C of the casing 1 to become a crank 3 </ b> A and the axis O 1 − of the drive shaft 3. O
The axis O2-O2 of the crank 3A is eccentric by a predetermined dimension .delta. The base end of the drive shaft 3 protruding out of the casing 1 from the bearing portion 1A is connected to a drive source (not shown), and the drive source 3 is driven to rotate by the drive source, thereby turning the drive shaft 3 through the crank 3A. The later-described orbiting scroll 7 is orbited. Reference numeral 6 denotes a balance weight fixed to the base end of the crank 3A. The balance weight 6 balances the rotation of the drive shaft 3 with respect to the orbital movement of the orbiting scroll 7.

Numeral 7 denotes a orbiting scroll which is located in the casing 1 and is provided at the tip of a crank 3A of the drive shaft 3. The orbiting scroll 7 is a disk-shaped end plate 7A.
And a spiral wrap portion 7B standing upright on the surface of the end plate 7A, with the center side being the winding start end and the outer peripheral side being the winding end end.
And a boss 7C provided at the center of the rear surface of the end plate 7A. And the orbiting scroll 7
Boss portion 7C protrudes toward the base end side of the casing 1,
In the boss 7C, a crank 3A of the drive shaft 3 is provided with a slewing bearing 8.
It is rotatably inserted through the. The back surface of the orbiting scroll 7 is opposed to the flange portion 1B of the casing 1 and has a flat surface 7D almost entirely.

Here, the wrap portion 7 of the orbiting scroll 7
B is disposed so as to overlap the wrap portion 2B of the fixed scroll 2 by a predetermined angle (for example, 180 degrees), and a plurality of wraps B are provided between the wrap portion 2B of the fixed scroll 2 and the wrap portion 7B of the orbiting scroll 7. The compression chambers 9, 9, ... are formed. During operation of the scroll-type air compressor, outside air is sucked into the compression chamber 9 on the outer peripheral side from the suction port 10 provided on the outer peripheral side of the fixed scroll 2, and the air is sucked while the orbiting scroll 7 rotates. While being sequentially compressed, is sent to the compression chamber 9 on the inner peripheral side, and finally the discharge port 11 provided at the center of the fixed scroll 2 from the compression chamber 9 on the center side.
To the outside via

Reference numerals 12, 12,... Denote support members arranged at four positions on the outer peripheral side of the flange portion 1B of the casing 1 as shown in FIG. And is disposed apart from each other in the up, down (Y-axis) direction and the left and right (X-axis) directions, and projects from the flange portion 1B of the casing 1 toward the rear side of the orbiting scroll 7 with a certain height dimension, The protruding end surface is a flat surface 12A. The support 12 is integrally formed with a Y-axis guide 15 for regulating the movement of the slider 16 to be described later in the left and right (X-axis) directions as a step extending in the upward and downward (Y-axis) directions.

Reference numeral 13 denotes a rotation preventing mechanism for preventing the orbiting scroll 7 from rotating. As shown in FIGS. 2 and 3, each X-axis guide 14, each Y-axis guide 15, and a slider 16, etc., as an Oldham coupling. The rotation preventing mechanism 13 slides and displaces the slider 16 in the X-axis and Y-axis directions, so that the orbiting scroll 7 integrated with each X-axis guide 14 is provided.
Of the rotation of the orbiting scroll 7 and the predetermined dimension δ
A circular motion having a turning radius of is given.

., X-axis guides provided on the back of the orbiting scroll 7, as shown in FIG. The orbiting scroll 7 projects from the rear face of the end plate 7A toward the flange portion 1B of the casing 1. The orbiting scroll 7 slides in the X-axis direction with respect to the slider 16 between the respective X-axis guides 14 separated in the Y-axis direction so that the respective side surfaces 16D of the slider 16 described later are slidably in contact with each other. It compensates for displacement.

Reference numerals 15, 15, ... denote Y-axis guides provided on the support 12, as shown in FIG. 2. Each of the Y-axis guides 15 is formed as a step extending in the upward and downward (Y-axis) directions. Then, the movement of the slider 16 described later in the left and right (X-axis) directions is regulated. A slider 16 described later is mounted between the Y-axis guides 15 separated in the X-axis direction.
As each side surface 16E of the slider 16 slides on each Y-axis guide 15, the slider 16
It compensates for sliding displacement in the axial direction.

Numeral 16 denotes a square ring-shaped slider provided between the casing 1 and the rear side of the orbiting scroll 7, and the slider 16 has upper and lower (Y-axis),
Four sliding parts 16A, 16A,... Formed as small rectangular parallelepiped pieces separated in the left and right (X-axis) directions, and four rod-like parts formed to connect the sliding parts 16A respectively. , And has a square shape as a whole. Each sliding portion 16A of the slider 16 has through holes 16C, 16C extending in the thrust direction.
C,... Are bored, and spheres 17 as rolling elements described later are inserted into the through holes 16C. Here, the inner diameter of each through hole 16C is formed to have a size larger than the diameter of each sphere 17 by the predetermined dimension δ.

As shown in FIG. 2, the slider 16 has opposite side surfaces 16D facing each other in the Y-axis direction.
4 are sliding surfaces against each other, and each side surface 1 opposed in the X-axis direction.
6E is a sliding surface for each Y-axis guide 15.
The slider 16 is guided in the X-axis direction with respect to the orbiting scroll 7 by each X-axis guide 14, and
Each Y-axis guide 15 guides the casing 1 in the Y-axis direction.

Reference numerals 17, 17,... Denote spheres as rolling elements inserted into the through holes 16C of the slider 16, and each sphere 17 is made of a wear-resistant metal material such as stainless steel, bearing steel or tool steel. Preferably, the ball is formed as a spherical ball from a hard metal material having a Rockwell C hardness of 55 or more, and has a diameter slightly larger than the axial dimension of each through hole 16C. Then, each sphere 17 comes into contact with each support plate 19, 21 provided between the flange portion 1 </ b> B of the casing 1 and the back surface of the orbiting scroll 7.
The thrust direction pressing force from the orbiting scroll 7 is received to compensate for the sliding displacement of the slider 16 and the orbiting scroll 7 smoothly in the X-axis and Y-axis directions.

Are fitting recesses formed as circular concave grooves on the flat surface 12A of each support 12 provided in the casing 1. Each fitting recess 18
At each position corresponding to the rolling locus, for example, each support 12 is formed with a diameter at least larger than the predetermined dimension δ, and each support plate 19 described later is fitted into each fitting recess 18.

Reference numerals 19, 19, ... denote bearing plates as first wear-resistant portions inserted into the respective fitting recesses 18 on the casing 1 side. The bearing plates 19 are hard and have a self-lubricating property. For example, it is formed in a disk shape by using a ceramic material such as partially stabilized zirconia,
8 is almost equal to the depth dimension. Each bearing plate 19 receives a pressing force in the thrust direction via each ball 17 together with a bearing plate 21 described later.

Reference numerals 20, 20,... Denote fitting concave portions formed as circular concave grooves on the flat surface 7D of the orbiting scroll 7.
Each support plate 21 described later is fitted in each fitting recess 20. Each fitting recess 20 is provided with each fitting recess 1.
8, the orbiting scroll 7 is formed at a position corresponding to the rolling trajectory of each ball 17 with, for example, a diameter at least larger than the predetermined dimension δ. It is inserted.

Reference numerals 21, 21,... Denote bearing plates as second wear-resistant portions inserted into the fitting recesses 20 on the orbiting scroll 7 side, and the bearing plate 21 is made of the same ceramic as the bearing plate 19. It is formed in a disk shape from a material, and its plate thickness is the same as the depth dimension of each of the fitting recesses 20, and receives a thrust direction pressing force via each sphere 17 together with the support plate 19 on the casing side. Things.

The scroll type air compressor according to the present embodiment has the above-described configuration. When the drive shaft 3 is rotated by driving the drive source, this rotation is performed by the crank 3A.
Is transmitted to the orbiting scroll 7 via the. This allows
The orbiting scroll 7 orbits with respect to the fixed scroll 2, compresses outside air sucked from the suction port 10 in each compression chamber 9, and discharges the air to the outside from the discharge port 11.

When the orbiting scroll 7 makes an orbital motion, the X-axis guide 14 and the Y-axis guide 15
The rotation of the orbiting scroll 7 is prevented by a rotation preventing mechanism 13 including a slider 16 and the like, and the orbiting scroll 7 is given a circular motion having a turning radius of a predetermined dimension δ around the drive shaft 3.

That is, while the orbiting scroll 7 orbits with respect to the fixed scroll 2, the slider 16 is displaced by sliding on one of the opposite side surfaces 16E along the respective Y-axis guides 15 provided on the flange portion 1B. As a result, the displacement in the X-axis direction is restricted, and the casing 1 is slid and displaced in the Y-axis direction. Also, the other opposing side surfaces 16
D is each X-axis guide 14 provided on the back of the orbiting scroll 7
Relative to the orbiting scroll 7 while the displacement in the Y-axis direction is regulated by the relative sliding displacement along the axis.

Each sphere 17 inserted into each through hole 16C of the slider 16 makes a circular motion with a diameter of a predetermined dimension δ on each support plate 19 of the casing 1, while it moves on each support plate 21 on the orbiting scroll 7 side. Predetermined dimension δ
Make a circular motion with the diameter of. Each sphere 17 receives a load in the thrust direction from the orbiting scroll 7 while rolling between the bearing plates 19 and 21 disposed on the casing 1 side and the back side of the orbiting scroll 7, respectively. The smooth displacement of the slider 16 is compensated for.

Thus, in this embodiment, the slider 16 is slidably disposed between the casing 1 and the back surface of the orbiting scroll 7, and the slider 16 is moved in the Y-axis direction by the Y-axis guides 15 on the casing 1 side. The orbiting scroll 7 is slid and displaced in the X-axis direction with respect to the slider 16 by the respective X-axis guides 14 on the orbiting scroll 7 side. Then, each through hole 16C of the slider 16
Each bearing plate 19, 21 accommodates each sphere 17 and is provided on the casing 1 side and the back side of the orbiting scroll 7, respectively.
Roll each sphere 17 between them.

As a result, the slider 16 is moved to each X-axis guide 1
4. By slidably engaging each of the Y-axis guides 15, the rotation of the orbiting scroll 7 can be prevented, and the orbiting operation of the orbiting scroll 7 can be compensated.
The slider 16 can be slid and displaced while smoothly rolling the respective spheres 17 between the support plates 19 and 21, and the pressing force from the thrust direction can be prevented from acting on the slider 16.

The sliding resistance generated between the front and rear surfaces of the slider 16 and the flat surfaces 12A and 7D of the casing 1 and the orbiting scroll 7 can be greatly reduced, and also occurs when the slider 16 slides. Wear can be reliably suppressed, and the slider 16 can be smoothly slid and displaced between the casing 1 and the back surface of the orbiting scroll 7.

Further, by forming the thrust bearing with the sphere 17 or the like inserted into each through hole 16C of the slider 16, it is possible to reliably receive the thrust direction pressing force from the orbiting scroll 7 during the compression operation. It is possible to prevent an extra load from acting on the slider 16 and the like,
The movement of the rotation preventing mechanism 13 composed of the Oldham coupling can be smoothed.

Further, the pressing force in the thrust direction is applied to each sphere 1
The bearing plates 19 and 21 received via the casing 7 are connected to the casing 1.
Since the casing 1 and the orbiting scroll 7 are formed as a separate member from the orbiting scroll 7, the casing 1 and the orbiting scroll 7 do not need to be formed of a hard material or the like, and the casing 1 and the orbiting scroll 7 can be formed of a relatively lightweight material. . Therefore, the degree of freedom in design and material selection is increased, the compressor is simple in structure, the number of parts is small, and a compressor excellent in workability and manufacturing cost can be realized. In addition, the entire scroll type air compressor can be reduced in size and weight. Can be easily implemented.

Furthermore, since each sphere 17 is formed of a hard metal material and each of the bearing plates 19 and 21 are formed of a hard and high wear-resistant ceramic material, the pressing force in the thrust direction is reduced. It is possible to reliably receive the two between them for a long period of time, and to smoothly roll each ball 17 between the support plates 19 and 21 without supplying a lubricant such as grease. Becomes easier.

Therefore, according to the present invention, each sphere 17 inserted into each through hole 16C of the slider 16 is rolled between the support plates 19 and 21, and each sphere 17 and each support plate 19 and 21 are rolled. Is formed of a ceramic material or the like having high strength and high wear resistance, the orbiting operation of the orbiting scroll 7 is stabilized, and the reliability and durability of the entire anti-rotation mechanism 13 including the slider 16 can be reliably improved. At the same time, the life of the scroll air compressor can be extended.

Further, since the pressing force from the thrust direction can be received by each sphere 17 or the like, the slider 16 and each X
The slider 16 and the orbiting scroll 7 can be smoothly slid without supplying a lubricant such as oil between the shaft guide 14 and each of the Y-axis guides 15. And a structure that does not particularly require a lubricant such as grease between the bearing and the bearing plates 19 and 21. Even when the compressor is applied to an oilless compressor, the scroll-type air compressor can be smoothly operated for a long period of time. Can be activated.

Next, FIG. 4 shows a second embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted. I do. However, a feature of this embodiment is that ring grooves 31 and 32 are formed on the peripheral wall surfaces of the fitting recesses 18 and 20, respectively.
Each of the O-rings 33 and 34 as an elastic member is mounted in the inside 32, and each of the disk-shaped bearing plates 19 and 21 is inserted into each of the fitting recesses 18 and 20 via the O-ring 33 and 34. I did it.

Here, the O-rings 33 and 34 are formed as annular rings having an inner diameter slightly smaller than the outer diameter of each of the support plates 19 and 21 by an elastic resin material.
The bearing plates 19, 21 are elastically supported so that the bearing plates 19, 21 are centered in the fitting recesses 18, 20, respectively.

Thus, in this embodiment constructed as described above, substantially the same functions and effects as those of the first embodiment can be obtained. In this embodiment, however, the bearing plates 19 and 21 are formed by the O-rings 33 and 34. Are resiliently supported in the fitting recesses 18 and 20, so that when each ball 17 rolls with the turning operation of the orbiting scroll 7, each bearing plate follows the rolling of the ball 17. It is possible to restrict the displacement of the balls 19 and 21 in the fitting recesses 18 and 20, and effectively suppress the generation of noise due to the rolling of the balls 17.

Next, FIG. 5 shows a third embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted. I do. However, this embodiment is characterized in that the ring grooves 43, 44 are formed on the outer peripheral surfaces of the bearing plates 41, 42 inserted into the fitting recesses 18, 20, respectively.
Each of the bearing plates 41, 4 is provided with the respective O-rings 45, 46 as elastic members mounted in the respective ring grooves 43, 44.
2 is inserted into each of the fitting recesses 18 and 20 respectively.

Here, each of the bearing plates 41 and 42 is formed in a disk shape from a ceramic material such as partially stabilized zirconia like the bearing plates 19 and 21 described in the first embodiment. Ring grooves 43,
44 is recessed. The O-rings 45 and 46 are formed of an elastic resin material as annular rings having an outer diameter slightly larger than the inner diameter of each of the fitting recesses 18 and 20. Each support plate 41, 42 is elastically supported so as to be centered within 18, 20.

Thus, in the present embodiment having the above-described structure, substantially the same operation and effect as those of the second embodiment can be obtained. In the present embodiment, in particular, each of the O-rings 45, Since the O-rings 46 are provided, the O-rings 45 and 46 can be easily mounted, and the workability and assemblability of the compressor can be improved.

FIGS. 6 and 7 show a fourth embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted. I do. However, the feature of this embodiment is that a ring-shaped groove 52 corresponding to the rolling locus R of each sphere 17 is provided on the surface side of each support plate 51 with which each sphere 17 slides, and follows the turning operation of the orbiting scroll 7. Thus, each of the spheres 17 is guided by each of the ring-shaped grooves 52.

Here, each support plate 51 is formed in a disk shape from a ceramic material such as partially stabilized zirconia like the support plates 19 and 21 described in the first embodiment, and each of the fitting recesses 18 and 21 is formed. 20. The ring-shaped groove 52 is an arc-shaped groove having a diameter slightly larger than the outer diameter of the sphere 17. The ring diameter of the ring-shaped groove 52 is, as shown in FIG. The predetermined dimension δ corresponds to the dynamic trajectory R. By providing each support plate 51 in each of the fitting recesses 18 on the casing 1 side and in each of the fitting recesses 20 of the orbiting scroll 7, the ring-shaped groove 52 of each support plate 51 And the orbiting scroll 7 with respect to each of the spheres 17 has a predetermined dimension δ.
This is to compensate for the circular motion.

Thus, in the present embodiment having the above-described structure, substantially the same operation and effect as those of the first embodiment can be obtained. In the present embodiment, in particular, the ring-shaped groove 52 is formed in each support plate 51. Provided along each ring-shaped groove 52,
, The contact surface pressure of each ball 17 can be reduced by increasing the sliding contact area between each ball 17 and each bearing plate 51. Therefore, even when a larger pressing force in the thrust direction is applied, it is possible to reliably receive the pressing force, and it is possible to prevent the spheres 17 and the support plates 51 from being worn by the pressing force in the thrust direction.

In each of the above embodiments, the sphere 17 is formed of a wear-resistant metal material such as stainless steel, bearing steel or tool steel, or a hard metal material having a Rockwell C hardness of 55 or more. (41, 42, 51) is formed of a ceramic material such as partially stabilized zirconia which is both hard and self-lubricating. However, the present invention is not limited to this. For example, each sphere 17 and each bearing The plates 19, 21 (41, 42, 51) may be formed of a ceramic material such as partially stabilized zirconia. Also,
Each sphere 17 and each support plate 19, 21 (41, 42, 5
1) is formed of a wear-resistant metal material such as stainless steel, bearing steel or tool steel, or a hard metal material having a Rockwell C hardness of 55 or more, and then filling each through hole 16C with a lubricant such as grease. The lubricity of each sphere 17 may be maintained.

In each of the above embodiments, a scroll type air compressor has been described as an example of a scroll type fluid machine. However, the present invention is not limited to this, and is widely applied to, for example, a vacuum pump, a refrigerant compressor and the like. The present invention can also be applied to a refueling scroll type fluid machine.

[0065]

As described above in detail, according to the first aspect of the present invention, the casing is slidably disposed between the casing and the back side of the orbiting scroll, and is spaced apart in the circumferential direction of the orbiting scroll. A slider provided with a plurality of through holes extending in the thrust direction, and the casing and the orbiting scroll inserted into each through hole of the slider so as to receive a load in the thrust direction from the orbiting scroll. A rolling element that is in rolling contact with the rear surface of the orbiting scroll, and a first and a second wear-resistant portion are provided on the casing side and the rear surface of the orbiting scroll at portions where the rolling elements contact each other. , The load in the thrust direction from the orbiting scroll can be reliably received between each rolling element and each wear-resistant portion, and
This load can be prevented from directly acting on the slider, and the sliding resistance applied to the slider between the casing and the orbiting scroll can be reliably reduced.

Further, the first and second wear-resistant portions can surely prevent wear on the casing side contacting each rolling element and the rear side of the orbiting scroll, so that each rolling element can be smoothly moved for a long period of time. It can be rolled, and the slidability of the slider can be greatly improved.

Further, since the first and second wear-resistant portions for receiving the pressing force in the thrust direction can be formed as separate members from the casing and the orbiting scroll, the entire casing and the orbiting scroll are formed with high strength. This eliminates the necessity, and the casing and the like can be formed of a light material. As a result, the degree of freedom in design and material selection is increased, a compressor having a simple structure, a small number of parts, and excellent workability and manufacturing cost can be realized. In addition, the overall size and weight of the scroll type air compressor can be reduced. Can be easily done.

Further, since the rolling element and the first and second wear-resistant portions can be formed of a material having high strength and lubricity, the rolling element can be formed without supplying a lubricant such as grease. , Can smoothly roll between the second wear-resistant parts,
The maintenance of the device is facilitated, and the scroll-type air compressor can be smoothly operated for a long period of time even when applied to an oilless compressor.

In this case, fitting recesses into which the first and second wear-resistant portions are inserted are formed on the casing side and the rear side of the orbiting scroll, respectively. Since an elastic member is provided between the fitting concave portion and each wear resistant portion to elastically support each wear resistant portion in each fitting concave portion, a load in the thrust direction from the orbiting scroll can be surely ensured. Each wear-resistant portion can be detachably provided at a contact portion of each rolling element rolling between the casing side and the back side of the orbiting scroll, and each wear-resistant portion is Displacement in the fitting concave portion can be restricted by the elastic member, and generation of noise due to rolling of each rolling element can be effectively suppressed.

Further, according to the third aspect of the present invention, at least one of the first and second wear resistant portions has a ring corresponding to the rolling locus of the rolling element. Since the ring-shaped concave groove having a diameter is formed, the first and second wear-resistant portions provided on the casing side and the orbiting scroll side and each rolling element can always be kept in a spherical contact state. By reducing the surface pressure, a large thrust load can be reliably received, and the rolling elements and the first and second wear resistant portions can be prevented from being worn by the thrust direction pressing force.

On the other hand, according to the invention described in claim 4,
Since at least one member of each of the rolling elements and each of the wear-resistant portions is formed of hard and partially stabilized zirconia having high wear resistance, it is not necessary to supply a lubricant such as grease. The rolling element can be smoothly rolled between the first and second wear-resistant portions, so that the maintenance of the device is easy and the scroll type air compressor is applicable even when applied to an oilless compressor. Can be operated smoothly over a long period of time.

According to the fifth aspect of the present invention,
Because at least one of the rolling elements and the wear-resistant portions is formed of a hard metal material having a Rockwell C hardness of 55 or more, and the rolling elements are lubricated with a lubricant. The load in the thrust direction from the orbiting scroll can be reliably received between each rolling element and each wear-resistant portion, and this load can be prevented from directly acting on the slider.
The sliding resistance applied to the slider between the casing and the orbiting scroll can be reliably reduced.

[Brief description of the drawings]

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

FIG. 2 is a sectional view taken in the direction of arrows II-II in FIG.

FIG. 3 is a sectional view taken in the direction of arrows III-III in FIG.

FIG. 4 is an enlarged cross-sectional view illustrating a slider, a sphere, a support plate, and the like of a scroll-type air compressor according to a second embodiment of the present invention;

FIG. 5 is an enlarged sectional view of a main part showing a slider, a sphere, a bearing plate and the like of a scroll type air compressor according to a third embodiment of the present invention.

FIG. 6 is a plan view showing a support plate used in a scroll type air compressor according to a fourth embodiment of the present invention.

FIG. 7 is a sectional view taken in the direction of arrows VII-VII in FIG. 6;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Casing 1B Flange part 2 Fixed scroll 3 Drive shaft 3A crank 7 Orbiting scroll 9 Compression chamber 12 Support body 13 Anti-rotation mechanism 14 X-axis guide 15 Y-axis guide 16 Slider 16C Through-hole 17 Spherical body (roller) 18, 20 Joint recesses 19, 21, 41, 42, 51 Bearing plate (wear-resistant portion) 31, 32, 43, 44 Ring groove 33, 34, 45, 46 O-ring (elastic member) 52 Ring-shaped groove R Rolling locus

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yoshio Kobayashi 1-6-3 Fujimi, Kawasaki-ku, Kawasaki City, Kanagawa Prefecture Tokiko Corporation (72) Inventor Hiroyuki Mihara 1-6-3, Fujimi, Kawasaki-ku, Kawasaki City, Kanagawa Prefecture No. Tokiko Co., Ltd. (72) Inventor Kazutaka Sueto 1-6-3 Fujimi, Kawasaki-ku, Kawasaki-shi, Kanagawa Pref.

Claims (5)

[Claims] 1. A casing, a fixed scroll provided integrally with the casing, a drive shaft having a base end rotatably supported by the casing and a distal end serving as a crank, and a pivotable crank on the drive shaft. A scroll type fluid machine comprising: a orbiting scroll that defines a plurality of compression chambers between the casing and the fixed scroll; and a rotation preventing mechanism that prevents rotation of the orbiting scroll. A slider provided with a plurality of through holes extending in the thrust direction and spaced apart in the circumferential direction of the orbiting scroll, and inserted into each of the through holes of the slider; A rolling element rotatably contacting the casing side and the rear side of the orbiting scroll so as to receive a load in the thrust direction from the scroll. On the back side of the casing and the orbiting scroll, the scroll type fluid machine which is characterized in that respective rolling elements are first each site in contact, and a configuration in which the second wear portion. 2. A fitting recess into which the first and second wear-resistant portions are inserted is formed on the casing side and a back side of the orbiting scroll, respectively. The scroll type fluid machine according to claim 1, further comprising an elastic member provided between the fitting recesses for elastically supporting each of the wear-resistant portions. 3. A ring-shaped concave groove having a ring diameter corresponding to a rolling locus of each of the rolling elements is formed in at least one of the first and second wear-resistant portions. The scroll-type fluid machine according to claim 1, wherein the scroll-type fluid machine is formed. 4. The scroll-type fluid machine according to claim 1, wherein at least one of the rolling elements and the wear-resistant portions is formed of partially stabilized zirconia. 5. A method according to claim 1, wherein at least one of the rolling elements and the wear-resistant parts is formed of a hard metal material having a Rockwell C hardness of 55 or more, and the rolling elements are lubricated with a lubricant. The scroll-type fluid machine according to claim 1, 2 or 3, wherein