JPH08319966A - Scroll type fluid machinery - Google Patents

Abstract

(57) [Summary] [Purpose] To effectively prevent the Oldham's joint from being worn or damaged at an early stage, to miniaturize the device, and to reliably improve the durability and life. [Structure] A slider 19 is slidably arranged between the casing 1 and the back side of the orbiting scroll 9, and the sliding displacement of the slider 19 is biaxial (X-axis) by each X-axis guide 17 and each Y-axis guide 18. , Y-axis) direction. The slide surface 3A of the flange portion 3 is inserted into each through hole 19B of the slider 19.
And the sliding surface 14B of the back plate 14 so as to rollably contact each other, each sphere 20 made of a material harder than the slider 19 is inserted, and grease (not shown) is sealed in each through hole 19B. . As a result, each sphere 20 smoothly rolls, and the frictional resistance between the both end surfaces of the slider 19 and each sliding surface 3A, 14B is significantly reduced.

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, and more particularly to an oilless scroll type fluid machine.

[0002]

2. Description of the Related Art Generally, a casing, a fixed scroll integrally provided on 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. A scroll-type fluid machine is known which includes an orbiting scroll that is orbitable and defines a plurality of compression chambers between the fixed scroll and a rotation preventing mechanism that prevents the orbiting scroll from rotating.

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 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.

[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 back side of the orbiting scroll and on the outer peripheral side of the orbiting bearing provided in 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, grease or the like is applied to the rotating portion of each auxiliary crank in order to maintain the lubricity of each auxiliary crank.

As another conventional technique, an Oldham coupling is used in a rotation preventing mechanism of a scroll type fluid machine, and the Oldham coupling has only a function of preventing rotation of an orbiting scroll. -378
No. 75 publication. Also, US Pat.
Japanese Patent No. 4635 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.
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 (Kokoku) No. 5-67761, it is composed of a large number of spheres and two ring-shaped plates having the same number of guide circular holes. There is disclosed 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 prior art described above, since a plurality of auxiliary cranks are employed as the rotation preventing mechanism, the cranks of the drive shaft and the eccentric dimensions of the auxiliary cranks match. Therefore, high-precision processing technology is required.

Even if the eccentric dimensions of the cranks are matched by design, it is difficult to balance the crank of the drive shaft and the auxiliary cranks due to the influence of centrifugal force due to the orbiting motion of the orbiting scroll, and vibration occurs. However, there is a problem in that it is difficult to actually design and manufacture the rotation preventing mechanism, and the structure becomes complicated and the number of parts increases.

Further, when the scroll type fluid machine according to the prior art is in operation, the pressure inside the compression chamber formed between the fixed scroll and the orbiting scroll becomes high, so that the orbiting scroll is pressed in the thrust direction. The thrust in the thrust direction acts as a load on the crank of the drive shaft and 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 drive shaft. There is a problem that abnormal wear of the crank and auxiliary crank and high temperature of friction heat are caused.

On the other hand, in the other anti-rotation mechanism using the Oldham coupling according to the prior art, in the Oldham coupling having only the anti-rotation function (see Japanese Patent Publication No. 6-37875), the thrust load of the orbiting scroll is applied. It is necessary to provide the bearing separately from the Oldham coupling, which causes a problem of increasing the size of the device. Further, in the Oldham joint having both the function of preventing rotation and the function of a thrust bearing (see US Pat. No. 3,994,635), the thrust force from the orbiting scroll directly acts on both surfaces of the Oldham joint, so There is a problem that the joint is apt to be worn during sliding, which causes deterioration of compression performance and the like.

Further, although the rotation prevention mechanism using this type of Oldham coupling has the advantages that the structure is relatively simple and the design and manufacturing are relatively easy, such an rotation prevention mechanism has an Oldham coupling. 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.

Further, as another conventional technique, in a rotation preventing mechanism using a ball coupling system (see Japanese Patent Publication No. 5-67761), it becomes difficult to position the orbiting scroll in the orbiting direction, and the size of the radial gap is increased. Is difficult to adjust with high precision, and it is difficult to block the noise generated from the sphere.

The present invention has been made in view of the above-mentioned problems of the prior art, and the present invention enables the rotation preventing mechanism composed of an Oldham coupling to be applied to an oilless type.
Provided is a scroll type fluid machine which can effectively prevent early wear and damage of the Oldham's joint during compression operation, can downsize the device, and can effectively improve durability and life. The purpose is to do.

[0014]

In order to solve the above-mentioned problems, the present invention provides a casing, a fixed scroll integrally provided in the casing, a base end side of which is rotatably supported by the casing, and a tip end thereof. A drive shaft whose side is a crank and a orbiting scroll that is provided on the crank of the drive shaft so as to orbit and that defines a plurality of compression chambers between the fixed scroll and a rotation preventing mechanism that prevents the orbiting scroll from rotating. It is applied to a scroll type fluid machine consisting of and.

A feature of the structure adopted by the invention of claim 1 is that the rotation preventing mechanism is arranged between the casing and the orbiting scroll and is slidable in two axial directions orthogonal to each other. The slider is provided with a plurality of through holes that are spaced in the circumferential direction of the orbiting scroll and are bored in the thrust direction, and the load in the thrust direction from the orbiting scroll is provided in each of the through holes. In order to receive the rolling elements, rolling elements that come into rolling contact with the casing and the rear side of the orbiting scroll are respectively inserted.

In this case, as in the invention described in claim 2, it is preferable that a lubricant for keeping each of the rolling elements in a lubricated state is enclosed in each of the through holes of the slider.

Further, as in the invention described in claim 3,
The slider may be provided with a passage portion through which cooling air flows at a position apart from the through holes in the circumferential direction of the orbiting scroll.

[0018]

With the above construction, in the invention described in claim 1,
When the slider slides in two axial directions, the rolling elements in the slider come into rolling contact with the rear side of the casing and the orbiting scroll, so that the frictional resistance received by the slider from the casing and the orbiting scroll is reduced. It can be reduced. Further, since the load in the thrust direction from the orbiting scroll is received by the slider and each rolling element in the slider, it is possible to prevent the load from directly acting on the slider.

In this case, as in the second aspect of the present invention, by enclosing a lubricant for keeping each of the rolling elements in a lubricated state in each of the through holes of the slider, each of the rolling elements has a casing and a swirl. The frictional resistance that occurs when rolling on the back side of the scroll can be reduced, which allows the slider to slide more smoothly, and reliably prevents wear and damage that occurs when the rolling elements roll. You can

According to the third aspect of the present invention, the cooling air is formed in the slider by forming a passage portion through which the cooling air flows in a position apart from the through holes in the circumferential direction of the orbiting scroll. Can be distributed to the back side of the orbiting scroll and the drive shaft through the passage portion,
As a result, frictional heat generated in the slider and the rolling elements when the slider slides can be surely radiated, and at the same time, the orbiting scroll and the drive shaft can be cooled.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 1 to 14 by taking an oil-free scroll type air compressor as a scroll type fluid machine.

1 to 4 show a first embodiment of the present invention.

In the drawings, reference numeral 1 denotes a stepped tubular casing forming an outer frame of a scroll type air compressor, and the casing 1 has a bearing portion 2 formed in a tubular shape having a small diameter and the bearing portion 2. An annular flange portion 3 that extends radially outward from the base end side, a cylindrical large diameter portion 4 that axially projects from the outer peripheral side of the flange portion 3, and a tip end of the large diameter portion 4. It is generally composed of an annular abutting portion 5 which further projects radially outward from the side.

Here, in the bearing portion 2 of the casing 1, a long small-diameter hole portion 2A into which a drive shaft 7 described later is inserted.
And a short large-diameter hole portion 2B that opens from the small-diameter hole portion 2A to the large-diameter portion 4 side of the casing 1. Inside the large-diameter hole portion 2B, a counterweight 8 and an orbiting scroll 9 described later are provided. The boss portion 14A and the like are accommodated. The inner side surface of the flange portion 3 of the casing 1 serves as a sliding surface 3A on which a slider 19 described later rolls, and each X-axis guide 17 described below is erected on the sliding surface 3A.

As shown in FIG. 2, the large-diameter portion 4 of the casing 1 has a cooling air intake 4A for circulating the cooling air into the casing 1, and a cooling air exhaust at a position facing the cooling air intake 4A. Outlets (not shown) are provided respectively, and bolt holes 5A, 5A for attaching a mounting flange portion 6B of a fixed scroll 6 described later to the abutting portion 5 of the casing 1 are provided.
... are drilled respectively.

Reference numeral 6 denotes a fixed scroll fixed to the front end side of the casing 1. The fixed scroll 6 is formed in a substantially disc shape and is arranged so that its center coincides with the axis O1 -O1 of the drive shaft 7. End plate 6A and a mounting flange portion 6B protruding from the outer edge side of the end plate 6A, the outer peripheral side being fixed to the abutting portion 5 of the casing 1 via bolts (not shown) or the like.
And a spiral wrap portion 6C which is axially erected from the front surface side of the end plate 6A, the center side of which is the winding start end and the outer peripheral side of which is the winding end end, and a large number of which are erected in parallel on the rear surface side of the end plate 6A. And heat dissipation plates 6D, 6D ,.

Reference numeral 7 denotes a drive shaft rotatably supported by a bearing in a small diameter hole 2A of the bearing 2 (casing 1), and the tip side of the drive shaft 7 has a large diameter hole of the bearing 2. The crank 7A extends into the portion 2B, and the axis O2 of the crank 7A
-O2 is a predetermined dimension δ with respect to the axis O1-O1 of the drive shaft 7.
Only eccentric. The drive shaft 7 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, so that the orbiting scroll 9 described later orbits through the crank 7A. .

Reference numeral 8 denotes a counter weight fixed to the base end side of the crank 7A. The counter weight 8 is located in the large diameter hole portion 2B of the bearing portion 2 and drives the drive shaft with respect to the orbiting movement of the orbiting scroll 9. Balances the rotation of the whole 7.

Reference numeral 9 denotes an orbiting scroll which is provided in the casing 1 so as to be capable of orbiting so as to face the fixed scroll 6,
The orbiting scroll 9 is an orbiting scroll body 10 described later.
And a substantially disk-shaped rear plate 14 attached to the rear side of the orbiting scroll body 10 as one body.

As shown in FIG. 2, the orbiting scroll body 10 has a disc-shaped end plate 10A, and an orbiting scroll main body 10 which is erected in the axial direction from the surface side of the end plate 10A and has a center side. A spiral wrap portion 10B having a winding start end and an outer peripheral end serving as a winding end, and a large number of heat radiating plates 10C, 10C, ... Standing in parallel on the back surface side of the end plate 10A. Here, as shown in FIG. 1, the wrap portion 10B of the orbiting scroll body 10 has a predetermined angle (for example, 1
The compression chambers 11 and 1 are arranged so as to overlap each other by shifting by 80 degrees), and between the lap portions 6C and 10B.
1, ... Are formed.

When the scroll type air compressor is in operation, the suction port 1 provided on the outer peripheral side of the fixed scroll 6 is operated.
2 while sucking air into the compression chamber 11 on the outer peripheral side, each of the compression chambers 1 is moved while the orbiting scroll 9 orbits this air.
1 is sequentially compressed, and finally compressed air is discharged from the compression chamber 11 on the center side to the outside through a discharge port 13 provided at the center of the fixed scroll 6.

Reference numeral 14 denotes a back plate provided on the back side of the orbiting scroll body 10.
Is formed in a disk shape having substantially the same diameter as the end plate 10A of the orbiting scroll main body 10, and a boss portion 14A is formed at the center of the rear surface of the rear plate 14 so as to project in the axial direction.
The back plate 14 is the orbiting scroll body 10.
Are fixed to the tip of each heat radiating plate 10C via bolts (not shown) or the like, and a plurality of cooling air passages A, A, ... By this, the rear side of the end plate 10A of the orbiting scroll body 10 can be efficiently cooled. Here, on the back side of the back plate 14, sliding surfaces 14B are provided between the Y-axis guides 18 described later, and the slider 19 slides on the sliding surfaces 14B.

The boss portion 14A of the back plate 14
Protrudes in the axial direction toward the bearing 2 side of the casing 1,
The boss portion 14A is attached to the crank 7A of the drive shaft 7 by the swivel bearing 1.
It is rotatably attached via 5.

Reference numeral 16 denotes a rotation prevention mechanism for preventing rotation of the orbiting scroll 9, and the rotation prevention mechanism 16 has X-axis guides 17, Y-axis guides 18 and sliders, which will be described later, as shown in FIGS. 19 and each spherical body 20, and by slidingly displacing the slider 19 in the X-axis and Y-axis directions, rotation of the orbiting scroll 9 integrated with each Y-axis guide 18 is prevented, and the orbiting scroll 9 is prevented from rotating. It is designed to give a circular motion (swing motion) having a turning radius of the predetermined dimension δ, and constitutes a so-called Oldham coupling.

Reference numerals 17 and 17 denote X-axis guides integrally provided on the sliding surface 3A of the flange portion 3 (casing 1), and each X-axis guide 17 has an elongated rectangular plate shape as shown in FIG. The drive shaft 7 is formed so as to be separated from the large-diameter hole portion 2B of the drive shaft 7 by a certain dimension in the Y-axis direction and extend parallel to the X-axis direction. Then, each side surface 19C of a slider 19 described later is mounted between the X-axis guides 17 so as to be in sliding contact therewith, and the slider 19 is restricted from slidingly displacing in the Y-axis direction with respect to the casing 1. .

Reference numerals 18 and 18 denote Y-axis guides integrally provided on the sliding surface 14B of the back plate 14 (orbiting scroll 9), and each Y-axis guide 18 has an elongated rectangular shape like the X-axis guide 17. It is formed in a plate shape, and is spaced from the boss portion 14A of the back plate 14 by a certain dimension in the X-axis direction and extends in parallel along the Y-axis direction. Then, between the Y-axis guides 18, side surfaces 19D of a slider 19 to be described later are mounted so as to be in sliding contact with each other, and the slider 19 is restricted from slidingly displacing in the X-axis direction with respect to the orbiting scroll 9. There is.

Reference numeral 19 denotes a slider slidably disposed between the flange portion 3 of the casing 1 and the back plate 14 of the orbiting scroll 9. The slider 19 is shown in FIG. Is formed in a substantially square flat plate shape, and an escape hole 19A through which the boss portion 14A of the back plate 14 penetrates is formed in the center thereof.
Is designed to prevent the slider 19 from colliding with the boss portion 14A when the slider 19 is slidably displaced. As shown in FIGS. 2 and 3, the four corners of the slider 19 are located on the outer peripheral side of the boss portion 14A of the back plate 14 and are spaced apart in the circumferential direction.
B, ... Are bored respectively, and each spherical body 20 is inserted in the through hole 19B together with grease described later.

Here, as shown in FIG. 3, in the slider 19, the side surfaces 19C and 19C facing each other in the Y-axis direction serve as sliding surfaces for the X-axis guides 17, and the side surfaces 19D and 19D facing each other in the X-axis direction are each. It is a sliding surface for the Y-axis guide 18. On the other hand, the front surface side and the back surface side of the slider 19 are sliding surfaces for the sliding surface 14B of the back plate 14 and the sliding surface 3A of the flange portion 3, respectively, and the thrust from the orbiting scroll 9 that occurs during compression operation. It is also a receiving surface that receives the pressing force in the direction.

The slider 19 is used for each X-axis guide 1
The sliding displacement direction is restricted in the X-axis direction with respect to the sliding surface 3A of the flange portion 3 by the back plate 1 and
The sliding displacement direction is restricted in the Y-axis direction with respect to the sliding surface 14B of No. 4.

Numerals 20, 20, ... Denote spherical bodies as rolling elements inserted into the through holes 19B of the slider 19, and each spherical body 20 is formed as a ball having a spherical diameter from a metal material harder than the slider 19. And its diameter is as shown in FIG.
The slider 19 is formed to have substantially the same size as the thickness of the slider 19.
Then, each through hole 19B of the slider 19 is provided with each sphere 20.
1 is housed in a substantially sealed state from both sides between the sliding surface 3A of the flange portion 3 and the sliding surface 14B of the back plate 14 as shown in FIG.

Here, grease (not shown) as a lubricant is enclosed in each through hole 19B of the slider 19,
As a result, when the front and back sides of the slider 19 slide on the sliding surfaces 3A and 14B, the spheres 20 are kept in a lubricated state and the spheres 20 smoothly move in the through holes 19B of the slider 19. I am able to roll. Further, each sphere 20 receives the thrust force from the orbiting scroll 9 in the thrust direction together with the front and back sides of the slider 19.

Reference numeral 21 denotes a cover provided on the back side of the fixed scroll 6, and the cover 21 is fixed to the tip of the heat radiating plate 6D of the fixed scroll 6 via a bolt (not shown), and each heat radiating plate 10C. Multiple cooling air passages B, B, ...
And the fixed scroll 6 by the cooling air from the outside.
The end plate 6A, the wrap portion 6C, and the like can be efficiently cooled.

Reference numeral 22 denotes a discharge pipe. The discharge pipe 22 has a base end side connected to the discharge port 13 at the center of the fixed scroll 6, and a tip end side penetrating the cover 21 to project to the outside and connected to an air tank or the like. There is.

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

First, when the drive shaft 7 is rotated by the electric motor to orbit the orbiting scroll 9, the wrap portion 6C of the fixed scroll 6 and the wrap portion 10B of the orbiting scroll 9 (orbiting scroll body 10) are defined. The compressed chambers 11, 11, ... Thereby, while the outside air sucked from the suction port 12 of the fixed scroll 6 is sequentially compressed in each compression chamber 11, the compressed air is discharged from the discharge port 13 of the fixed scroll 6 to the external air tank via the discharge pipe 22. Store.

When the orbiting scroll 9 makes an orbiting motion in this manner, the X-axis guide 17 and the Y-axis guide 1
The rotation of the orbiting scroll 9 is prevented by the rotation preventing mechanism 16 including the slider 8, the spheres 20, and the like.
The orbiting scroll 9 has a predetermined size δ around the drive shaft 7.
A circular motion (turning motion) is given with a turning radius of.

That is, while the orbiting scroll 9 orbits with respect to the fixed scroll 6, one side surface 19C of the slider 19 slides on the side surface of the X axis guide 17 to move in the Y axis direction. While the displacement is regulated, the casing 1 is slidably displaced in the X-axis direction in FIG.
Further, the other side surfaces 19D facing each other are provided on the respective Y-axis guides 18
The displacement in the X-axis direction is regulated by sliding on the side surface, while the orbiting scroll 9 is displaced in the Y-axis direction. The front surface and the back surface side of the slider 19 are
The sliding surface 3 </ b> A of the flange portion 3 and the sliding surface 14 </ b> B of the back plate 14 respectively slide and receive a load in the thrust direction together with the spherical bodies 20.

Here, each through hole 19 of the slider 19 is
Since each sphere 20 is inserted into B, each sphere 20 is brought into rolling contact with each sliding surface 3A, 14B, and grease is enclosed in each through hole 19B, The slider 19 can slide the sliding surfaces 3A and 14B while smoothly rolling the spherical bodies 20.

As a result, the frictional resistance generated between the front and back surfaces of the slider 19 and the respective sliding surfaces 3A and 14B can be greatly reduced, and the abrasion generated when the slider 19 slides can be effectively suppressed. Therefore, the slider 19 can be slid smoothly between the sliding surfaces 3A and 14B.

When the front surface and the back surface side of the slider 19 slightly wears while the slider 19 repeats the sliding motion, each sphere 20 is harder than the slider 19, so that only each sphere 20 is moved to each sliding surface. 3A and 14B can be brought into contact with each other, and thereby the front surface and the back surface of the slider 19 can be reliably prevented from further wearing.

The front surface and the back surface side of the slider 19 can receive the load (pressing force) in the thrust direction from the orbiting scroll 9 generated during the compression operation together with each sphere 20,
As a result, wear and damage of the slider 19 can be prevented more effectively.

Furthermore, since each through hole 19B of the slider 19 is kept in a substantially sealed state by each sliding surface 3A, 14B, it is possible to effectively prevent the internal grease from leaking to the outside. With each through hole 19
It is possible to block the rolling noise of each sphere 20 from leaking to the outside from inside B, and it is possible to effectively reduce the noise from the device.

Thus, in this embodiment, the slider 19 is slidably disposed between the casing 1 and the rear surface of the orbiting scroll 9, and the slider 19 is slid by the X-axis guides 17 and the Y-axis guides 18. The dynamic displacement is regulated in the two-axis (X, Y-axis) directions, and each through hole 19B of the slider 19 is rotatably brought into contact with the sliding surface 3A of the flange portion 3 and the sliding surface 14B of the back plate 14. Each sphere 20 is inserted together with grease, and each sphere 20 is made of a material harder than the slider 19.

As a result, by smoothly rolling the spheres 20, the frictional resistance between the front and back surfaces of the slider 19 and the sliding surfaces 3A and 14B can be greatly reduced. The wear between the sliding surfaces 3A and 14B can be effectively prevented, and the slider 1
The front surface and the back surface of 9 can receive the thrust force from the orbiting scroll 9 together with the respective spherical bodies 20, whereby the slider 19 can be more effectively prevented from being worn or damaged. .

Therefore, according to the present invention, the slider 19
The rolling motion of each sphere 20 on each sliding surface 3A, 14B can surely improve the durability of the slider 19, prolong the life of the scroll type air compressor, and surely improve the performance. At the same time, stable compression performance can be secured for a long period of time.

Further, the thrust bearing that receives the load (pressing force) in the thrust direction from the orbiting scroll 9 can be compactly formed by the slider 19 and each spherical body 20,
The size of the entire device can be reduced.

Further, the slider 19 and each sliding surface 3A, 1
4B, the slider 19, each X-axis guide 17, each Y
Even if a lubricant such as oil is not supplied to the shaft guide 18, the sliders 19 can be smoothly slid between the casing 1 and the back side of the orbiting scroll 9 by the spherical bodies 20, and no oil is supplied. The scroll type air compressor can be smoothly operated as a rotary compressor.

Next, FIGS. 5 and 6 show a second embodiment of the present invention. In this embodiment, the same components as those of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. It shall be. However, the feature of this embodiment is that the slider 32 of the rotation prevention mechanism 31 slidably arranged between the casing 1 and the rear side of the orbiting scroll 9 has a rectangular thick portion 32.
A and each thin thin portion 32B for connecting them to each other
And between the thin portions 32B and the sliding surface 3A of the flange portion 3 and between the thin portions 32B and the back plate 14.
.. are formed between the sliding surface 14B and the sliding surface 14B.

Here, although the slider 32 has substantially the same structure as the slider 19 described in the first embodiment,
The slider 32 is formed in a substantially square shape, and a square escape hole 32C is provided inside. As shown in FIGS. 5 and 6, the slider 32 is composed of thick-walled portions 32A, 32A, ... Located at the four corners and thin-walled portions 32B, 32B ,. The adjacent side surfaces of the thick portion 32A are sliding surfaces for the X-axis guides 17 and the Y-axis guides 18, respectively.

The front surface and the back surface side of each thick portion 32A serve as sliding surfaces for the respective sliding surfaces 3A and 14B, and four through holes 32D and 3 are formed in the thick portion 32A.
Each sliding surface 3 together with each sphere 20 inserted in 2D, ...
It slides on A and 14B. Further, the slider 32 has tapered slant portions 32E, 32E, ... Between the thick portions 32A and the thin portions 32B, and the slider 32 is provided between the slant portions 32E on the front surface and the back surface side of each thin portion 32B. Passage portions 33, 33 are provided between the sliding surfaces 3A, 14B for circulating cooling air.

Thus, in this embodiment having the above-described structure, it is possible to obtain substantially the same effect as that of the first embodiment. However, particularly in this embodiment, the slider 32 and each sliding surface 3A, Since each passage portion 33 for cooling air is formed between the passage portion 14B and 14B, the cooling air can be circulated in each passage portion 33 as shown in FIG. As a result, when the slider 32 slides, frictional heat generated between the sliding surfaces 3A and 14B and the side surfaces of the X-axis guide 17 and the Y-axis guide 18 can be effectively cooled, and the sliders can be effectively cooled. The durability of 32 can be reliably extended.

Further, the swirl bearing 15 and the like in the boss portion 14A can be simultaneously cooled by this cooling air, and the swirl bearing 15 and the like are damaged early due to frictional heat generated by the rotational movement of the drive shaft 7. It is possible to effectively prevent it from happening, and it is possible to extend the durability and life of the device.

Next, FIGS. 7 and 8 show a third 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. It shall be. However, the feature of this embodiment is that the slider 42 constituting the rotation preventing mechanism 41 is composed of the thick portions 42A and the thin portions 42B connecting them to each other, and the slider 42
A circular relief hole 42C is provided in the central portion of.

Here, the slider 42 has thick portions 42A and 4A similar to the slider 42 described in the second embodiment.
2A, ... and thin portions 42B, 42B ,.
The spherical body 20 is accommodated in each through hole 42D, and passage portions 43, 43, ... Are formed between the inclined portions 42E on the front surface and the back surface side of each thin portion 42B. However, a circular escape hole 42C is formed in the center of the slider 42.
Has been pierced large.

Thus, in this embodiment having the above-described structure, it is possible to obtain substantially the same operation and effect as in the second embodiment, but especially in this embodiment, the escape hole 42C of the slider 42 is made larger. By forming a circular shape,
A part of the cooling air flowing in the X and Y directions shown by the arrow can be made to flow between the escape hole 42C of the slider 42 and the boss portion 14A of the back plate 14, so that the cooling efficiency can be improved.

Next, FIGS. 9 to 11 show a fourth embodiment of the present invention. In this embodiment, the same components as those of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. It shall be. However, the feature of this embodiment is that the rotation prevention mechanism 51
Is formed integrally with the slider 52,
Each X-axis key 53A, each Y-axis key 53B, and each X-axis key 53 that regulates the sliding displacement of the slider 52 in the two-axis (X, Y-axis) directions between the casing 1 and the rear side of the orbiting scroll 9.
A, key groove 4 in each X-axis direction that engages with each Y-axis key 53B
4A, each Y-axis direction keyway (not shown) and each sphere 20.

Here, although the slider 52 is formed in substantially the same manner as the slider 19 shown in the first embodiment, the slider 19 is made of a disk-shaped plate material as shown in FIG. A relief hole 52A is formed in the portion,
Each through hole 52B, 52 into which each sphere 20 is inserted in the circumferential direction
B, ... Are drilled respectively. In addition, the slider 52
As shown in FIGS. 10 and 11, a pair of X-axis keys 53A, 53A are integrally formed on the back side along the X-axis direction, and a pair of Y-axis keys 53A and 53A are integrally formed on the front side along the Y-axis direction. 5
3B and 53B are integrally formed.

On the other hand, on the sliding surface 3A side of the flange portion 3 of the casing 1, as shown in FIG.
Key grooves 54A, 5 in the X-axis direction corresponding to the shape of A
4A is formed, and Y is formed on the sliding surface 14B of the back plate 14 so as to correspond to the shape of the keys 53B in the Y-axis directions.
A shaft keyway is formed.

Then, each X-axis key 53A of the slider 52
Is slid in each key groove 54A of the sliding surface 3A, thereby restricting the slider 52 from slidingly moving in the Y-axis direction with respect to the sliding surface 3A. Also, each Y of the slider 52
By sliding the shaft key 53B in each key groove of the sliding surface 14B, the slider 52 is restricted from slidingly moving in the X-axis direction with respect to the orbiting scroll 9.

Thus, also in this embodiment having the above-mentioned structure, the slider 52 moves each spherical body 20 onto each sliding surface 3A, 14A.
The respective sliding surfaces 3A, 14B can be slid while making rolling contact with B, and substantially the same effect as that of the first embodiment can be obtained.

Next, FIG. 12 shows a fifth embodiment of the present invention. In this embodiment, the same components as those in the fourth 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 slider 52 located around each through hole 52B has a ring-shaped edging portion 61, 61, ...
Is provided, and each of the edging portions 61 is axially projected from the front surface and the back surface of the slider 52, so that each of the edging portions 61 is formed.
The end surface of the rear surface plate 14 and the sliding surface 3A of the flange portion 3
Of the slider 52 and the sliding surfaces 3A, 14B around the respective rim portions 61, and passages 62, 62, ... For circulating cooling air are formed between the slider 52 and the sliding surfaces 3A, 14B. Especially.

Thus, also in this embodiment having the above-described structure, the cooling air can be circulated in the direction of the arrow C or the like by the passage portions 62, and the same effect as that of the second embodiment can be obtained. be able to.

Next, FIG. 13 shows a sixth embodiment of the present invention. In this embodiment, the same components as those in the fourth embodiment are designated by the same reference numerals and the description thereof will be omitted. To do. However, the feature of the present embodiment is that the X-axis keys 53A and the Y-axis keys 53B described in the fourth embodiment are replaced with keys in the X-axis direction on the front surface side and the back surface side of the slider 52, respectively. Grooves 71A, 71A and key grooves 71B, 71B in the Y-axis direction are formed, and the sliding surface 3A of the flange portion 3 and the sliding surface 14B of the back plate 14 are made to correspond to the key grooves 71A, 71B.
And X-axis keys and Y-axis keys (neither of which are shown) are formed respectively.

Thus, also in this embodiment having such a configuration, the slider 52 of the rotation preventing mechanism 51 is attached to the casing 1.
And the rear side of the orbiting scroll 9, the respective spherical bodies 20 can be slid while making rolling contact, and substantially the same effect as that of the first embodiment can be obtained.

Next, FIG. 14 shows a seventh embodiment of the present invention. In this embodiment, the same components as those in the fourth 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 key grooves 81A and 81A in the X-axis direction and the key grooves 81B and 81B in the Y-axis direction are formed on the front surface side and the back surface side of the slider 52, respectively. , 81B and each through hole 52B are provided with a plurality of passage portions 82, 82, which are spaced apart from each other in the circumferential direction, and are provided in the slider 52 via each passage portion 82, for example, as indicated by an arrow D. , E and F directions are provided to circulate the cooling air.

Thus, in this embodiment having the above-described structure, it is possible to obtain substantially the same effect as that of the fifth embodiment.

In each of the above embodiments, the slider 19
Each through hole 19B (32D, 42) in (32, 42, 52)
However, the present invention is not limited to this, and for example, five or more through holes may be provided so as to be spaced apart from each other in the circumferential direction of the orbiting scroll 9, or three through holes may be provided. The through hole may be provided. And
When the number of through holes is increased, the slider 19 (3
2, 42, 52) can be slid more smoothly on the sliding surfaces 3A, 14B, and each slider 19 (3
(2, 42, 52) can be surely prevented from being worn and damaged, and the external force acting on each sphere 20 can be reduced, so that the durability of the sphere 20 can be surely enhanced.

In each of the above-mentioned embodiments, grease is enclosed in the sphere 20 to enhance the lubricity of the sphere 20, but instead of this, the sphere 20 and the slider 19 (32,
42, 52) and the like are formed from a material having self-lubricating property,
The lubricity of the sphere 20 may be enhanced, or the sphere 2
0 may be entirely made of ceramic or the like to be completely unlubricated, or only the outer peripheral side of the spherical body 20 may be made of ceramic or the like to be completely unlubricated.

Furthermore, although the scroll type air compressor has been described as an example of the scroll type fluid machine in the above embodiment, the present invention is not limited to this, and for example, a vacuum pump,
It can be widely applied to refrigerant compressors and the like.

[0080]

As described in detail above, according to the invention described in claim 1, the slider is slidably disposed in the two axial directions orthogonal to each other between the casing and the orbiting scroll, and is rotated by the slider. In addition to constituting a prevention mechanism, the slider is provided with a plurality of through holes spaced in the circumferential direction of the orbiting scroll and bored in the thrust direction, and the thrust direction from the orbiting scroll is provided in each of the through holes. In order to receive the load, since the rolling elements which are rotatably in contact with the casing and the rear side of the orbiting scroll are respectively inserted, the sliders are formed by rolling the rolling elements. The slider can be smoothly slid with the orbiting scroll, the wear of the slider between the casing and the orbiting scroll can be effectively prevented, and the orbiting scroll can be effectively prevented. The load in the thrust direction from the roll can be received by each rolling element, the durability and life of the slider can be reliably extended, the reliability of the device can be improved, and stable operation for a long time can be achieved. Can be guaranteed.

Further, since the load in the thrust direction from the orbiting scroll can be received by each rolling element together with the slider, it is not necessary to separately provide a thrust bearing, and the entire device can be made compact and downsized. Can be planned.

According to the second aspect of the invention, the lubricant leaks from the through holes by making the through holes of the slider substantially sealed between the casing and the back side of the orbiting scroll. It is possible to prevent the rolling noise, and to effectively block the rolling noise when each rolling element rolls, and reduce the noise from the device. Since the lubricity of each rolling element can be effectively improved, the slider can be slid more smoothly, and the performance of the device can be greatly improved.

Further, according to the invention described in claim 3,
By circulating the cooling air through the passage formed in the slider, frictional heat generated by sliding the slider,
Friction heat and the like generated between the drive shaft and the orbiting scroll due to the rotation of the drive shaft can be effectively cooled, whereby the life of the device can be greatly extended.

[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 exploded perspective view showing a casing, an orbiting scroll, a rotation preventing mechanism and the like in FIG.

3 is an enlarged plan view showing the slider and each sphere in FIG. 1. FIG.

FIG. 4 is an enlarged sectional view taken along the line IV-IV in FIG.

FIG. 5 is a plan view similar to FIG. 3, showing a second embodiment of the present invention.

FIG. 6 is an enlarged sectional view taken along the line VI-VI in FIG.

FIG. 7 is a plan view similar to FIG. 3, showing a third embodiment of the present invention.

8 is an enlarged cross-sectional view taken along arrow VIII-VIII in FIG.

FIG. 9 is an external view showing a state in which a slider of a scroll type air compressor according to a fourth embodiment of the present invention is arranged in a casing.

FIG. 10 is an enlarged plan view showing the slider and each sphere in FIG.

11 is an enlarged cross-sectional view taken along line XI-XI in FIG.

FIG. 12 is an exploded perspective view of a slider and a sphere showing a fifth embodiment of the present invention.

FIG. 13 is a perspective view similar to FIG. 12, showing a sixth embodiment of the present invention.

FIG. 14 is a perspective view similar to FIG. 12, showing a seventh embodiment of the present invention.

[Explanation of symbols]

 1 Casing 3 Flange 3A Sliding Surface 6 Fixed Scroll 7 Drive Shaft 7A Crank 11 Compression Chamber 9 Orbiting Scroll 14 Back Plate 14B Sliding Surface 16, 31, 41, 51 Rotation Preventing Mechanism 17 X Axis Guide 18 Y Axis Guide 19, 32, 42, 52 Slider 19B, 32D, 42D, 52B Through hole 20 Sphere (roller) 33, 43, 62, 82 Passage part

 ─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Yoshio Kobayashi 1-3-6 Fujimi, Kawasaki-ku, Kawasaki City, Kanagawa Prefecture Tokiko Corporation (72) Hiroyuki Mihara 1-3-6 Fujimi, Kawasaki-ku, Kawasaki City, Kanagawa Prefecture No. Tokiko Co., Ltd. (72) Inventor Shunji Suzuki 1-3-6 Fujimi, Kawasaki-ku, Kawasaki-shi, Kanagawa Tokiko Co., Ltd.

Claims (3)

[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 the scroll type fluid machine, which comprises a revolving scroll that defines a plurality of compression chambers between the revolving scroll and the fixed scroll, and a rotation preventing mechanism that prevents rotation of the revolving scroll, the rotation preventing mechanism is the casing. And a orbiting scroll, the slider being slidable in two axial directions orthogonal to each other. The slider is provided with a plurality of holes spaced in the circumferential direction of the orbiting scroll and provided in the thrust direction. Through holes, and in each of the through holes, the casing and the orbiting scroll are received in order to receive the load in the thrust direction from the orbiting scroll. A scroll-type fluid machine characterized in that rolling elements that come into rolling contact with the back side of the roll are inserted. 2. The scroll fluid machine according to claim 1, wherein a lubricant that keeps each of the rolling elements in a lubricated state is enclosed in each of the through holes of the slider. 3. The scroll fluid machine according to claim 1, wherein the slider is formed with a passage portion through which cooling air flows in a position apart from each of the through holes in a circumferential direction of the orbiting scroll. .