JPH0988849A - Scroll type fluid machinery - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability and the service life by smoothing the operation of a rotation preventing mechanism so as to be applicable even to an oil-less type. SOLUTION: An Oldham's ring 20 is slidably arranged between a flange part 6 of a casing 5 and a back plate of a turning scroll, the Oldham's ring 20 is slidably displaced in the X-axis direction by each X-axis key groove 26 on the casing 5 side, and the turning scroll is slidably displaced in the Y-axis direction relative to the Oldham's ring 20 by each Y-axis key groove on the turning scroll side. A plurality of thrust bearings 28, 28... consisting of each ball 29 and each ball storage cylinder 30 are provided between key supporting parts 21, 23 on the outer side in the radial direction of the Oldham's ring 20, and grease is sealed around each ball 29 in the ball storage cylinder 30 of each thrust bearing 28.

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 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.

[0004] Here, it is known that an oil-free scroll type fluid machine uses a plurality of auxiliary cranks in order to prevent the orbiting scroll from rotating. 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. In the case of the rotation preventing mechanism of each auxiliary crank of this type, in order to maintain the lubricity of each auxiliary crank, a lubricant such as grease is applied to the rotating portion of each auxiliary crank.

Further, as another conventional technique, for example, US Pat. No. 3,994,635 discloses an Oldham joint having both a function of preventing rotation of an orbiting scroll and a function of receiving a thrust load of the orbiting scroll. There is. Then, in the case of the rotation preventing mechanism by the Oldham coupling of this type, in order to maintain the lubricity of the Oldham coupling, the lubricating oil is constantly supplied to the sliding portion of the Oldham coupling.

Further, as another conventional rotation preventing mechanism, for example, in Japanese Examined Patent Publication No. 5-67761, the sphere is composed of a large number of spheres and two ring-shaped plates having the same number of guide circular holes. Discloses a ball coupling system having both the function of preventing rotation of the orbiting scroll and the function of a thrust bearing against the thrust load of the orbiting scroll.

[0007]

By the way, in the scroll type fluid machine according to the above-mentioned prior art, for example, when the scroll type fluid machine is used as a scroll type compressor, the compression chamber formed between the fixed scroll and the orbiting scroll is Because of the high pressure, the orbiting scroll is pressed in the thrust direction. The thrust force in the thrust direction (axial direction) acts as a load on each of the auxiliary cranks, increases the rotational friction of the crank of the drive shaft and each of the auxiliary cranks, reduces the drive performance, and reduces the auxiliary cranks. There is a problem of causing abnormal wear and high temperature of friction heat.

On the other hand, in the other prior art, although the Oldham joint has both the rotation preventing function and the thrust bearing function, the thrust force (axial direction) from the orbiting scroll is directly applied to both surfaces of the Oldham joint. Since it works, the Oldham coupling is apt to be worn during sliding, which causes a problem such as deterioration in performance during compression operation.

Further, the rotation preventing mechanism using this type of Oldham coupling has the advantages that the structure is relatively simple and the design and manufacturing are relatively easy. However, in such a rotation preventing mechanism, the Oldham coupling is used. Lubricating oil must be constantly supplied to the sliding parts and the like, and it can be applied to a refueling type scroll fluid machine, but it is difficult to apply to a non-lubricating type.

Furthermore, as another conventional technique, in a rotation preventing mechanism using a ball coupling system, it is difficult to accurately adjust the radial clearance dimension, and noise generated from a sphere is blocked. There is a problem that it is difficult.

The present invention has been made in view of the problems of the prior art as described above, and the present invention provides an anti-rotation mechanism composed of an Oldham coupling and a thrust bearing for receiving a load in the thrust direction independently. Provide a scroll type fluid machine that can smooth the operation of the Oldham coupling side, can be applied to a non-lubricated type, can surely improve durability and life, and can improve reliability. Is intended.

[0012]

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.

A feature of the configuration adopted by the invention of claim 1 is that the rotation preventing mechanism is provided with a first joint guide provided on the casing side and a second joint guide provided on the rear side of the orbiting scroll. And a movable joint that is disposed between the casing and the back side of the orbiting scroll and slidably engaged with the first and second joint guides, respectively, and One of the orbiting scrolls is provided with a plurality of thrust bearings located between the first and second joint guides and receiving a thrust load from the orbiting scroll by bringing a rolling element into contact with the other end. There is something.

As a result, the load in the thrust direction (axial direction) from the orbiting scroll can be prevented from acting on the movable joint or the like of the rotation preventing mechanism, and the load between the first and second joint guides and the movable joint can be prevented. Sliding resistance can be reliably reduced. Further, the rolling element of each thrust bearing can be stably rolled between the casing and the orbiting scroll without being affected by the rotation prevention mechanism, and the movement as the thrust bearing can be smoothed.

Further, in the invention described in claim 2, each of the thrust bearings is arranged so as to be rollable between the casing and the rear side of the orbiting scroll, and a spherical body constituting the rolling element, and the casing. Alternatively, it is configured by a spherical body containing cylinder formed in a tubular shape so as to protrude from the orbiting scroll in the axial direction and surround the spherical body from the outside.

With this structure, the movement of each sphere when rolling can be stabilized between the casing and the back side of the orbiting scroll, and the rolling noise (sliding sound) of each sphere can be stabilized. Etc. can be insulated by the spherical container.

Further, in the invention described in claim 3, the movable joint is formed by an Oldham ring extending in the circumferential direction between the casing and the rear side of the orbiting scroll and provided with Oldham keys on both axial ends. Configure and
The first and second joint guides extend in two axial directions orthogonal to each other so that the Oldham keys of the Oldham ring can be slidably mounted, and the Oldham ring with respect to the spherical housing cylinders of the thrust bearings. The first and second key grooves are spaced apart in the circumferential direction.

With this configuration, the rotation preventing mechanism (Oldham coupling) can be smoothly moved, and the spherical accommodating cylinders of the thrust bearings can be separated from the first and second key grooves in the circumferential direction. It can be disposed, and it is possible to reliably prevent the thrust load from the orbiting scroll from acting between each Oldham key and each key groove.

Further, in the invention as set forth in claim 4, a plurality of ring bodies are integrally formed on the Oldham ring between the Oldham keys, and the ring bodies are orbited by the orbiting scroll. The spherical accommodating cylinders are surrounded from the outside so as not to interfere with the spherical accommodating cylinders of the thrust bearings during operation.

As a result, when the orbiting scroll orbits, the respective ring bodies of the Oldham ring can be relatively orbited on the outside of the respective sphere containing cylinders, and the ring bodies are interposed in the middle of the Oldham ring. The thrust bearing (sphere housing cylinder) can be compactly arranged.

[0021]

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

1 to 3 show a first embodiment in which the scroll fluid machine of the present invention is applied to an oil-free scroll air compressor.

In the figure, reference numeral 1 denotes an electric motor which is a drive source of the scroll air compressor, and the electric motor 1 includes a motor case 2 forming an outer frame thereof, and the motor case 2.
The rotor 3 is rotatably provided inside and a drive shaft 4 for outputting the rotation from the rotor 3 to the outside. The drive shaft 4 of the electric motor 1 projects into a casing 5 described later, and the tip end side thereof is a crank 4A that is eccentric by a predetermined dimension δ with respect to the axis of the drive shaft 4 as shown in FIG. Further, the motor case 2 is configured to sandwich the casing 5 with a fixed scroll 11 described later.

Reference numeral 5 denotes a cylindrical casing forming an outer frame of the scroll air compressor, and the casing 5 has an annular flange portion 6 arranged between the casing 5 and the motor case 2.
And a cylindrical bearing portion 7 provided on the inner peripheral side of the flange portion 6 and a large-diameter cylindrical portion 8 axially extending from the outer peripheral side of the flange portion 6, and the bearing of the casing 5 Part 7
A bearing 9 that rotatably supports the drive shaft 4 of the electric motor 1 is attached to the shaft.

Reference numeral 10 denotes a balance weight located inside the motor case 2 and fixed to the drive shaft 4. The balance weight 10 balances the rotation of the entire drive shaft 4 with respect to the orbiting movement of the orbiting scroll 12 described later. ing.

Reference numeral 11 denotes a fixed scroll fixed to the front end side of the casing 5, and the fixed scroll 11 is an end plate 11A which is formed in a substantially disc shape and is arranged so that its center coincides with the axis of the drive shaft 4. And a mounting flange portion 11B protruding from the outer edge side of the end plate 11A and having an outer peripheral side fixed to the tip of the large-diameter cylindrical portion 8 of the casing 5 via a bolt or the like (not shown), and a front surface side of the end plate 11A. A spiral wrap portion 11C that is erected in the axial direction from the center side and has a winding start end on the center side and a winding end end on the outer side, and a large number of heat radiating plates 11D that are erected in parallel on the back side of the end plate 11A and extend in parallel with each other It consists of and.

Reference numeral 12 denotes an orbiting scroll which is provided in the casing 5 so as to be orbitable so as to face the fixed scroll 11, and the orbiting scroll 12 is attached to an orbiting scroll body 13 which will be described later and a rear side of the orbiting scroll body 13. And a substantially disc-shaped back plate 17 formed integrally.

Reference numeral 13 is an orbiting scroll body, and the orbiting scroll body 13 is provided with an end plate 13A formed in a disk shape and axially erected from the surface side of the end plate 13A, with the center side being the winding start end and the outer peripheral side being wound. The spiral wrap portion 13B which is the end end and a large number of heat radiating plates 13C, 13C, ... Standing in parallel on the back surface side of the end plate 13A are generally configured.

Here, the wrap portion 13B of the orbiting scroll body 13 has a fixed scroll 11 as shown in FIG.
Are arranged so as to be offset from each other by a predetermined angle (for example, 180 degrees), and a plurality of compression chambers 14, 14, ... Are formed between the two lap portions 11C, 13B. Then, when the scroll air compressor is in operation, the suction port 15 provided on the outer peripheral side of the fixed scroll 11 is provided.
While sucking air into the compression chambers 14 on the outer peripheral side from the compression chambers 1 while the orbiting scroll 12 orbits the air.
4 is sequentially compressed, and finally compressed air is discharged from the compression chamber 14 on the center side to the outside through a discharge port 16 provided at the center of the fixed scroll 11.

Reference numeral 17 denotes a back plate provided on the back side of the orbiting scroll main body 13, the back plate 17 is formed in a disk shape, and a boss portion 17A is projected in the axial direction at the center of the back surface of the back plate 17. Has been formed. And
The back plate 17 is fixed to the tip of each heat radiating plate 13C of the orbiting scroll body 13 via a bolt (not shown) or the like so that the orbiting scroll body 13 orbits.

Here, the boss portion 17A of the back plate 17
Protrudes in the axial direction toward the bearing portion 7 side of the casing 5, and the boss portion 17A is rotatably attached to the crank 4A of the drive shaft 4 via a swivel bearing 18. Further, on the back surface side of the back plate 17, the portions located between the Y-axis key grooves 27 described later become the sliding surfaces 17B, 17B, ..., respectively, and the respective spheres 29 described later roll on the sliding surfaces 17B. It is possible to contact.

Reference numeral 19 denotes an Oldham coupling as a rotation preventing mechanism for preventing the orbiting scroll 12 from rotating, and the Oldham coupling 19 is, as shown in FIGS. 2 and 3, an Oldham ring 20, each X-axis key 22, which will be described later. Each Y-axis key 24 and each key groove 26, 27 are configured. The Oldham coupling 19 slides and displaces the Oldham ring 20 in the X-axis direction, and the orbiting scroll 12 is slidably displaced in the Y-axis direction with respect to the Oldham ring 20 to prevent the orbiting scroll 12 from rotating. At the same time, the orbiting scroll 12 is given a circular motion (orbiting motion) having a turning radius of the predetermined dimension δ.

Reference numeral 20 denotes an Oldham ring which constitutes a movable joint of the Oldham joint 19. The Oldham ring 20 has an inner peripheral side thereof as an escape hole 20A for the boss portion 17A of the back plate 17, and the escape hole 20A is the Oldham ring 20. When the boss slides in the X-axis and Y-axis directions, the boss 17
In order to prevent the collision with A, it is formed with a relatively large hole diameter. The Oldham ring 20 is formed as a circular ring made of a high-strength metal plate or the like, and each X-axis key supporting portion 21 and each Y-axis key supporting portion 23 described later are integrally formed on the outer peripheral side thereof.

Reference numerals 21 and 21 denote a pair of X-axis key support portions that project radially outward from the outer peripheral side of the Oldham ring 20 and extend in the X-axis direction. X-axis keys 22, 22 extending in the X-axis direction are integrally provided, and each X-axis key 22 projects toward the flange portion 6 side of the casing 5 with a certain height from the axial end surface of the Oldham ring 20, It is slidably engaged with an X-axis key groove 26 described later.

Reference numerals 23 and 23 denote a pair of Y-axis key support portions that project radially outward from the outer peripheral side of the Oldham ring 20 and extend in the Y-axis direction, and each Y-axis key support portion 23 supports each X-axis key support. Each key support portion 2 is formed in the same shape as the portion 21.
Numerals 1 and 23 project from the Oldham ring 20 in a cross shape. Then, Y-axis keys 24, 24 extending in the Y-axis direction are integrally provided on the tip end side of each Y-axis key support portion 23, and each Y-axis key 24 is a scroll scrolling more than the axial end surface of the Oldham ring 20. 12 back plates 1
It projects toward the 7 side and slidably engages with each Y-axis key groove 27 described later.

25 and 25 are flange portions 6 of the casing 5.
2 shows a flat plate-shaped guide integrally provided on the inner side surface 6A of each of the guides 25. Each of the guides 25 extends in the X-axis direction along the inner side surface 6A of the flange portion 6.

Reference numerals 26 and 26 denote X-axis key grooves as first joint guides provided in the guides 25. The X-axis key grooves 26 extend in the X-axis direction along the guides 25. Is formed as. Then, each X-axis key groove 26
The X-axis key 22 of the Oldham ring 20 is slidably engaged to guide the Oldham ring 20 in the X-axis direction.

Reference numerals 27 and 27 denote Y-axis key grooves as a second joint guide formed on the back plate 17 of the orbiting scroll 12, and each Y-axis key groove 27 is a back plate 17.
Is formed as a concave groove that is located on the back side of and extends in the Y-axis direction. The Y-axis key grooves 27 are slidably engaged with the Y-axis keys 24 of the Oldham ring 20 and guide the orbiting scroll 12 with respect to the Oldham ring 20 in the Y-axis direction. .

28, 28, ... are the orbiting scrolls 12
2 shows thrust bearings for receiving the thrust load from the above, each thrust bearing 28 is rotatably arranged between the flange portion 6 of the casing 5 and the back plate 17 of the orbiting scroll 12, and the thrust load It is composed of a spherical body 29 as a rolling element to be received, and a spherical body accommodating cylinder 30 axially protruding from the flange portion 6 of the casing 5 and formed in a cylindrical shape so as to surround each spherical body 29 from the outside. ing.
Then, each of the spherical body housing cylinders 30 has a projecting dimension slightly smaller than the diameter of the spherical body 29 and has an inner surface 6A of the flange portion 6.
To the rear plate 17 side, and the front end side thereof is an open end and is arranged to face each sliding surface 17B of the rear plate 17. Further, as shown in FIG. 2, the respective spherical body housing cylinders 30 are disposed between the respective key support portions 21 and 23 on the outer side in the radial direction of the Oldham ring 20, and between the respective spherical body housing cylinders 30 the Oldham ring 20 and the respective key support portions. It is configured to allow the 21, 23 to be displaced in the X-axis direction.

Here, each sphere 29 is formed of a steel ball or the like having a high rigidity, and can roll (slide) between the bottom of each sphere housing cylinder 30 and each sliding surface 17B of the back plate 17. It is arranged. The inner diameter of each sphere container 30 is formed to be larger than the diameter of each sphere 29 by the predetermined dimension δ to compensate for each sphere 29 rolling smoothly following the orbiting movement of the orbiting scroll 12. There is.

In addition, grease (not shown) serving as a lubricant may be filled around the sphere 29 in each sphere accommodating cylinder 30, and this grease may be present between the sliding surface 17B of the back plate 17. It is kept almost sealed in. Then, when each sphere 29 is relatively slidably displaced on the sliding surface 17B of the back plate 17 together with each sphere housing cylinder 30,
The grease keeps each sphere 29 in a lubricated state and smoothly rolls each sphere 29 in each sphere housing cylinder 30.

The scroll air compressor according to this embodiment has the above-mentioned structure, and its operation will be described below.

First, when the drive shaft 4 is rotated by the electric motor 1 and the orbiting scroll 12 is orbited, an image is formed between the wrap portion 11C of the fixed scroll 11 and the wrap portion 13B of the orbiting scroll 12 (orbiting scroll body 13). The compression chambers 14, 14, ... Created continuously shrink. As a result, the compressed air is stored in the external air tank or the like from the discharge port 16 of the fixed scroll 11 while sequentially compressing the outside air sucked from the suction port 15 of the fixed scroll 11 in each compression chamber 14.

When the orbiting scroll 12 revolves in this manner, the Oldham coupling 19 including the Oldham ring 20, each X-axis key groove 26, each Y-axis key groove 27, etc. prevents the orbiting scroll 12 from rotating. The orbiting scroll 12 is given a circular motion (orbiting motion) having a orbiting radius of a predetermined dimension δ about the drive shaft 4.

That is, while the orbiting scroll 12 orbits with respect to the fixed scroll 11, the Oldham coupling 19
The X-axis keys 22 on the Oldham ring 20 side are slidably displaced along the X-axis key grooves 26 on the casing 5 side to restrict the displacement in the Y-axis direction, and Sliding displacement in the axial direction. Also, the Y-axis keys 24 of the Oldham ring 20 are the Y-axis keys on the orbiting scroll 12 side.
The relative sliding displacement along the axial key groove 27 allows the orbiting scroll 12 to perform sliding displacement in the Y-axis direction.

On the inner surface 6A of the flange portion 6 of the casing 5, each key support portion 2 of the Oldham ring 20 is provided.
, 23 (each key groove 26, 27) located between 1 and 23 and projecting axially toward the back plate 17 side are integrally formed with a total of four sphere housing cylinders 30, 30 ,. Since the thrust bearing 28 is configured by accommodating the spherical body 29 together with the grease therein, the spherical body 29 of each thrust bearing 28 is slidable between the bottom portion (casing 5) of the spherical body accommodating cylinder 30 and the back plate 17. By sliding (rolling) following the movement of the orbiting scroll 12 with the moving surface 17B, the load in the thrust direction from the orbiting scroll 12 can be received by each sphere 29, and the Oldham ring of the Oldham coupling 19 is received. It is possible to compensate for smooth sliding displacement of 20 and the like in the X-axis and Y-axis directions.

Thus, according to this embodiment, the Oldham ring 20 is slidably arranged between the flange portion 6 of the casing 5 and the back plate 17 of the orbiting scroll 12.
The Oldham ring 20 is slidably displaced in the X-axis direction by the X-axis key grooves 26 on the casing 5 side, and the orbiting scroll 1
The orbiting scroll 12 is slidably displaced in the Y-axis direction with respect to the Oldham ring 20 by the Y-axis key grooves 27 on the second side. A plurality of thrust bearings 28 each including a sphere 29 and a sphere accommodating cylinder 30 are provided radially outside the Oldham ring 20 and between the key support portions 21 and 23.
28 are provided, and the spherical body housing cylinder 3 of each thrust bearing 28 is provided.
Grease is enclosed in the circumference of each sphere 29 in the 0.

As a result, the spherical body 29 of each thrust bearing 28 is
The sliding surface 1 of the orbiting scroll 12 (back plate 17)
Each thrust bearing 2 while rolling smoothly against 7B
X-axis key 2 of Oldham ring 20 provided independently of 8
2, Y-axis key 24, X-axis key groove 26, Y-axis key groove 27
By slidably engaging the orbiting scroll 12 with each other, rotation of the orbiting scroll 12 can be prevented, the orbiting operation of the orbiting scroll 12 can be stabilized, and the thrust load from the orbiting scroll 12 generated during compression operation can be applied to each sphere. 29, the thrust load can be securely received, and the thrust load can be prevented from acting on the Oldham coupling 19 side.

Then, it occurs between each X-axis key 22 and each Y-axis key 24 on the Oldham ring 20 side, each X-axis key groove 26 on the casing 5 side, and each Y-axis key groove 27 on the back plate 17 side. The sliding resistance can be suppressed to be small, and the wear generated when the Oldham ring 20 is slid can be effectively reduced, and the X-axis keys 22 of the Oldham ring 20 can be moved along the X-axis key grooves 26 in the X-axis direction. The Y-axis key 24 allows the orbiting scroll 12 to move through the Y-axis key groove 27.
On the other hand, it can be slidably displaced in the Y-axis direction.

Further, each spherical body accommodating cylinder 30 provided integrally with the flange portion 6 of the casing 5 is axially projected toward the back plate 17 side, and the projecting dimension thereof is slightly smaller than the diameter of the spherical body 29. Therefore, it is effective that the tip end side (opening end) of each sphere containing cylinder 30 is closed by the sliding surface 17B of the back plate 17 and the grease in each sphere containing cylinder 30 leaks to the outside. Therefore, the spheres 29 in the sphere housing cylinders 30 can be kept in a lubricated state for a long period of time.

The thrust load (pressing force) from the orbiting scroll 12 generated during the compression operation can be reliably received by each sphere 29 between the casing 5 and the back plate 17, and an extra load is applied to the Oldham coupling 19 and the like. It can be surely prevented from acting, and each sphere 29 as a rolling element
It is possible to stabilize the movement of the ball when it rolls between the casing 5 and the back plate 17, and to prevent the rolling sound of the ball 29 and the like from being blocked by the ball housing cylinder 30.

Therefore, according to this embodiment, the casing 5
Side and the orbiting scroll 12 side, the Oldham coupling 19 and each thrust bearing 28 can be completely separated (independent) to operate, and the thrust load from the orbiting scroll 12 causes the Oldham ring 20 of the Oldham coupling 19 or the like. Can be prevented and the sliding resistance between each X-axis key 22, each Y-axis key 24 and each X-axis key groove 26, each Y-axis key groove 27 of the Oldham ring 20 can be significantly reduced. The durability and life of the Oldham coupling 19 and the like can be reliably extended.

Further, the spherical body 29 of each thrust bearing 28 can be smoothly rolled between the casing 5 and the orbiting scroll 12 without being influenced by the Oldham's joint 19, and the spherical body 29 is housed in each spherical body housing cylinder 30. Each of the thrust bearings 28 is held by keeping each sphere 29 in a lubricated state by the enclosed grease.
In addition to reliably improving the life and durability of the scroll air compressor, the life of the scroll air compressor can be extended and the performance can be reliably improved, and stable compression performance can be secured for a long period of time.

Further, a lubricating oil such as oil is specially supplied between each X-axis key 22, each Y-axis key 24 and each X-axis key groove 26, each Y-axis key groove 27 on the Oldham ring 20 side. The Oldham ring 20 and the like can be smoothly slidably displaced between the casing 5 and the back side of the orbiting scroll 12 without needing to smoothly operate the scroll air compressor as an oil-free compressor. There is an effect such as being able to.

Next, FIGS. 4 and 5 show an oil-free scroll air compressor according to a second embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are the same. The reference numerals are given and the description thereof is omitted. But,
The feature of the present embodiment is that an Oldham ring 41, which is a movable joint of the Oldham joint 19, is provided integrally with four ring divided bodies 42, 42, ... ., And the thrust bearings 28 are formed by the respective ring bodies 43.
The spherical container cylinders 30 are arranged so as to surround them from the outside.

Here, each ring divided body 42 of the Oldham ring 41 constitutes a circular ring as a whole by connecting each ring divided body 43 to each other, and among the ring divided bodies 42 in the X-axis direction in FIG. Opposing ring division 4
A pair of X-axis keys 44, 44 projecting in the axial direction toward the flange portion 6 side of the casing 5 are integrally provided in 2, 42. Further, a pair of Y-axis keys 45, 45 projecting toward the rear plate 17 side of the orbiting scroll 12 in the Y-axis direction in FIG. 5 are integrally provided. And each X
The axis keys 44 and the Y-axis keys 45 are the same as the X-axis keys 22 and the Y-axis keys 24 described in the first embodiment, the X-axis key grooves 26 and the orbiting scroll 12 on the casing 5 side.
Each of the Y-axis key grooves 27 on the side is slidably engaged.

On the other hand, each ring body 4 of the Oldham ring 41
3, the inner diameter is formed larger than the outer diameter of each sphere housing cylinder 30 by the predetermined dimension δ, and while the Oldham ring 41 is displaced in the X-axis direction with respect to the casing 5 by the orbiting operation of the orbiting scroll 12, It is designed to prevent each ring body 43 from colliding with each spherical body housing cylinder 30. Each ring body 43 is formed to have substantially the same height (thickness) as that of each ring division body 42, and the Oldham ring 41 smoothly slides between the casing 5 and the orbiting scroll 12 (relative displacement). I am compensated for doing this.

Thus, in this embodiment having such a structure, it is possible to obtain substantially the same operational effects as in the first embodiment, but particularly in this embodiment, the thrust bearings 28 as shown in FIG. 4 are obtained. Each ring body 43 surrounding the sphere housing cylinder 30 of FIG.
Since the orbiting scroll 12 orbits and the Oldham ring 41 as a whole slides and displaces in the X-axis direction with respect to the casing 5, since the orbiting scroll 12 is integrally provided between the two ring bodies 43, the respective sphere housing cylinders 30 are provided. Displacement on the outside of the can eliminate the problem of interference (collision) between the two,
The thrust bearings 28 can be compactly arranged in the middle of the Oldham ring 41 via the ring bodies 43, and the scroll air compressor can be made smaller and lighter.

Next, FIGS. 6 and 7 show an oil-free scroll compressor according to a third embodiment of the present invention. In this embodiment, the same components as those in the first embodiment have the same reference numerals. Will be attached and the description thereof will be omitted. However, the feature of the present embodiment is that the Oldham ring 51, which is a movable joint of the Oldham joint 19, is formed with a diameter dimension substantially corresponding to the back plate 17 (orbiting scroll 12), and each thrust bearing 28 is provided in the Oldham ring 51. It is configured to accommodate.

Here, on the inner peripheral side of the Oldham ring 51, a pair of X-axis key support portions 52, 52 extending inward in the radial direction along the X-axis direction, and the respective X-axis key support portions 5 are provided.
The X-axis key 53 located on the tip end side of 2 and protruding in the axial direction toward the flange portion 6 side of the casing 5, and the pair of X-axis keys 53 extending inward in the radial direction from the inner circumference of the Oldham ring 51 along the Y-axis direction. The Y-axis key support portions 54, 54 are integrally provided with a Y-axis key 55 located on the tip end side of each Y-axis key support portion 54 and protruding in the axial direction toward the back plate 17 side. Then, each X-axis key 53 and each Y-axis key 55 are constructed in substantially the same manner as the X-axis key 22 and the Y-axis key 24 described in the first embodiment, and each X-axis key groove 2 on the casing 5 side.
6. The Oldham ring 51 is relatively displaced in the X-axis and Y-axis directions along the Y-axis key grooves 27 on the orbiting scroll 12 side.

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 each of the above-mentioned embodiments, the lubricant (grease) is enclosed together with the sphere in each sphere container, but the present invention is not limited to this, and the grease or the like is not necessarily contained in each sphere container. It is not necessary to enclose the lubricant.

Further, in each of the above-mentioned embodiments, the scroll air compressor has been described as an example of the scroll type fluid machine, but the present invention is not limited to this and can be widely applied to, for example, a vacuum pump, a refrigerant compressor and the like. .

[0064]

As described in detail above, according to the first aspect of the invention, the rotation preventing mechanism is provided with the first joint guide provided on the casing side and the first joint guide provided on the rear side of the orbiting scroll. And a movable joint which is disposed between the casing and the back side of the orbiting scroll and slidably engaged with the first and second joint guides, respectively. One of the orbiting scrolls is provided with a plurality of thrust bearings that are located between the first and second joint guides and that receive a thrust load from the orbiting scroll by bringing a rolling element into contact with the other end. Since it is configured, the movable joint of the rotation preventing mechanism and each thrust bearing can be operated independently, and the sliding resistance between the first and second joint guides and the movable joint can be ensured. It can be reduced.

Further, the rolling element of the thrust bearing can be stably rolled between the casing and the orbiting scroll without being affected by the rotation preventing mechanism, and the movement as the thrust bearing can be smoothed. Further, the reliability of the device can be improved, stable operation can be compensated for a long period of time, and the device can be easily applied to an oil-free scroll type fluid machine.

In this case, as in the second aspect of the present invention, each thrust bearing is provided so as to be rollable between the casing and the rear side of the orbiting scroll, and a spherical body forming the rolling element, Since it is composed of a sphere accommodating cylinder formed in a cylindrical shape so as to project from the casing or the orbiting scroll in the axial direction and surround the sphere from the outside, the sphere rolls between the casing and the back side of the orbiting scroll. The movement when moving can be stabilized, and the rolling sound (sliding sound) of the sphere can be insulated by the sphere housing cylinder. Further, since the thrust bearing is integrally formed on the casing side or the orbiting scroll side, it is possible to effectively prevent the lubricant such as grease enclosed in each of the spherical body containing cylinders from leaking to the outside, and the spherical body The sphere can be kept in a lubricated state in the housing cylinder for a long period of time.

Further, according to the third aspect of the present invention,
The movable joint is constituted by an Oldham ring that extends in the circumferential direction between the casing and the back side of the orbiting scroll and is provided with Oldham keys at both ends in the axial direction, and the first and second joint guides are Each Oldham key of the Oldham ring extends in two axial directions orthogonal to each other so that the Oldham keys are slidably mounted, and is separated from the spherical accommodating cylinder of each thrust bearing in the circumferential direction of the Oldham ring. Since it is configured by the key groove, the movement as the rotation preventing mechanism (Oldham joint) can be smoothed, and the spherical bearing accommodating cylinder of the thrust bearing can be arranged in the circumferential direction away from the first and second key grooves. It is possible to reliably prevent the thrust load from the orbiting scroll from acting between the Oldham keys and the key grooves.

Further, according to the invention as set forth in claim 4, a plurality of ring bodies are integrally formed on the Oldham ring between the Oldham keys, and the ring bodies are
Since the spherical accommodating cylinders of the thrust bearings are surrounded from the outside so as not to interfere with the spherical accommodating cylinders of the thrust bearings during the orbiting operation of the orbiting scroll, each Oldham ring of the Oldham ring is rotated when the orbiting scroll orbits. The ring body can be relatively displaced outside each sphere housing cylinder, the movements of the Oldham ring and the thrust bearings (spheres) can be stabilized, and the thrust is inserted at an intermediate part of the Oldham ring via each ring body. The bearing (spherical cylinder) can be compactly arranged.

[Brief description of drawings]

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

2 is an enlarged sectional view taken along line II-II in FIG. 1 showing the casing, the Oldham coupling, and the thrust bearing in a state where the back plate of the orbiting scroll and the like are removed.

FIG. 3 is an external view showing an Oldham ring and the like of an Oldham coupling viewed from the back side of a back plate (orbiting scroll).

FIG. 4 is an enlarged cross-sectional view showing a casing, an Oldham coupling, and a thrust bearing of a scroll air compressor according to a second embodiment of the present invention at the same position as in FIG.

FIG. 5 is an external view similar to FIG. 3, showing a back plate (orbiting scroll) of a scroll air compressor according to a second embodiment of the present invention, an Oldham ring of an Oldham coupling, and the like.

FIG. 6 is an enlarged cross-sectional view showing the casing, Oldham coupling, and thrust bearing of the scroll air compressor according to the third embodiment of the present invention at the same position as in FIG.

FIG. 7 is an external view similar to FIG. 3, showing a back plate (orbiting scroll) of a scroll air compressor according to a third embodiment of the present invention, an Oldham ring of an Oldham coupling, and the like.

[Explanation of symbols]

 4 Drive shaft 4A Crank 5 Casing 6 Flange part 11 Fixed scroll 11A, 13A End plate 11C, 13B Wrap part 12 Orbiting scroll 13 Orbiting scroll body 14 Compression chamber 17 Back plate 17A Boss part 17B Sliding surface 19 Oldham joint (rotation prevention mechanism) 20,41,51 Oldham ring (movable joint) 22,44,53 X-axis key 24,45,55 Y-axis key 26 X-axis key groove (joint guide) 27 Y-axis key groove (joint guide) 28 Thrust bearing 29 Sphere (Rolling body) 30 Sphere housing cylinder 42 Ring division body 43 Ring body

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Yoshio Kobayashi Yoshio Kobayashi 1-6-3 Fujimi, Kawasaki-ku, Kanagawa Prefecture Tokiko Corporation (72) Hiroyuki Mihara 1-6-3 Fujimi, Kawasaki-ku, Kanagawa Prefecture Issue Tokiko Co., Ltd.

Claims (4)

[Claims] 1. A casing, a fixed scroll integrally provided in the casing, a drive shaft having a base end side rotatably supported by the casing and a tip end serving as a crank, and a crank of the drive shaft. In a scroll type fluid machine comprising an orbiting scroll that defines a plurality of compression chambers between the fixed scroll and a fixed scroll, and a rotation preventing mechanism that prevents rotation of the orbiting scroll, the rotation preventing mechanism is the casing. A first joint guide provided on the side, a second joint guide provided on the back side of the orbiting scroll, and the first and second portions provided between the casing and the back side of the orbiting scroll. And a movable joint slidably engaged with the joint guides of the first and second casings, respectively. Located between the two joint guide, scroll fluid machine which is characterized in that a plurality of thrust bearings that receive a thrust load from said orbiting scroll by contacting the rolling elements in the other party. 2. Each of the thrust bearings is a sphere that is rotatably arranged between the casing and the back side of the orbiting scroll and constitutes the rolling element, and an axially protruding portion from the casing or the orbiting scroll. The scroll type fluid machine according to claim 1, wherein the scroll type fluid machine comprises a spherical body containing cylinder formed in a cylindrical shape so as to surround the spherical body from the outside. 3. The movable joint comprises an Oldham ring extending in the circumferential direction between the casing and the back side of the orbiting scroll, and Oldham keys are provided on both axial ends of the Oldham ring. Of the Oldham ring extends in two axial directions orthogonal to each other so that the Oldham keys of the Oldham ring can be slidably mounted, and is separated from the spherical housing cylinder of the thrust bearing in the circumferential direction of the Oldham ring. 3. A structure comprising first and second keyways.
The scroll-type fluid machine described. 4. The Oldham ring is integrally formed with a plurality of ring bodies located between the Oldham keys, and the ring bodies are spherical accommodating cylinders of the thrust bearings when the orbiting scroll orbits. The scroll fluid machine according to claim 3, wherein the spherical container is surrounded from the outside so as not to interfere with the scroll type fluid machine.