JP2002285979A - Scroll-type fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily attach balance weight on a drive shaft, in a manner such that the balance weight is prevented from turning, for improving assembling workability and reducing the manufacturing cost. SOLUTION: A rotary shaft part engaging hole 25A engaging with a shaft end part 10C of a rotation shaft part 10 provided on a drive shaft 9, and an eccentric shaft part engaging hole 25C, engaging with an eccentric shaft part 11, are provided on an attachment cylinder part 25 of the balance weight 24. Since the attachment cylinder part 25 can be attached on the drive shaft 9, in a manner such that the balance weight is prevented from turning by using the rotation shaft part 10 and the eccentric shaft part 11 provided eccentrically on the drive shaft 9, the balance weight 24 can be easily attached by merely engaging the attachment cylinder part 25 from a tip side of the drive shaft 9 without screws, a key or the like separately.

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 an air compressor, a vacuum pump and the like.

[0002]

2. Description of the Related Art In general, a scroll type fluid machine generally includes a stationary member including a casing and a fixed scroll provided in the casing, a rotating shaft portion rotatably provided in the casing, and a rotating shaft portion. A drive shaft including an eccentric shaft portion eccentrically provided on the distal end side, and a orbiting scroll that is rotatably provided on the eccentric shaft portion of the drive shaft and defines a plurality of compression chambers between the fixed scroll and the drive shaft. And a balance weight which is provided so as to be fitted to the distal end side of the drive shaft and balances the rotation of the drive shaft when the orbiting scroll is turned.

Here, the balance weight applies a predetermined load to the eccentric shaft portion with respect to the rotating shaft portion in a direction opposite to the eccentric direction. It is necessary to mount in a state where it is positioned in the rotation direction with respect to the rotation direction.

In such a conventional scroll type fluid machine, when the rotating shaft of the drive shaft is rotated, the orbiting scroll orbits with a certain eccentric dimension with respect to the fixed scroll by the eccentric shaft. Accordingly, fluid such as air sucked from the suction port is sequentially compressed in the compression chamber defined between the fixed scroll and the orbiting scroll to become a compressed fluid, and is discharged from the discharge port to the outside.

[0005]

By the way, in the scroll type fluid machine according to the prior art described above, a screw, a key and the like are used as means for attaching the balance weight to the drive shaft in a non-rotating state. For this reason, when the balance weight is mounted on the drive shaft, parts such as screws and keys are separately required, and a screw hole into which the screw is screwed, a key groove into which the key is mounted, and the like are also required.

As a result, the number of parts and the number of processing steps required for attaching the balance weight to the drive shaft are increased, resulting in a problem that the assembling workability is reduced and the manufacturing cost is increased.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems of the prior art, and it is an object of the present invention to easily mount a balance weight on a drive shaft in a non-rotating state, thereby improving assembling workability. Another object of the present invention is to provide a scroll type fluid machine capable of reducing the manufacturing cost.

[0008]

According to the present invention, there is provided a scroll-type fluid machine comprising: a fixed-side member including a casing and a fixed scroll provided in the casing; and a rotating shaft portion rotatably provided in the casing. A plurality of compression chambers are defined between a drive shaft composed of an eccentric shaft portion eccentrically provided on the distal end side of the rotary shaft portion and a rotatable pivot shaft mounted on the eccentric shaft portion of the drive shaft. And a balance weight that is provided to be fitted to the tip end of the drive shaft and that balances the rotation of the drive shaft when the orbiting scroll is turned.

Then, in order to solve the above-mentioned problem,
The feature of the configuration adopted by the invention of claim 1 is that the fitting hole of the balance weight has a rotating shaft fitting hole fitted to the rotating shaft of the drive shaft and an eccentric shaft fitting fitted to the eccentric shaft. It consists of a hole.

With this configuration, the rotary shaft fitting hole is fitted to the rotary shaft of the drive shaft, and the eccentric shaft fitting hole is fitted to the eccentric shaft. At this time, since the two shaft portions and the fitting holes are eccentrically arranged, by fitting them together, the balance weight can be attached to the drive shaft in a detented state.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a scroll type air compressor will be described in detail as an example of a scroll type fluid machine according to an embodiment of the present invention with reference to the accompanying drawings.

First, FIGS. 1 to 3 show a first embodiment of the present invention. Reference numeral 1 denotes a casing forming an outer frame of the scroll-type air compressor. The casing 1 constitutes a fixed-side member together with a fixed scroll 5 described later, and is disposed horizontally so that the axis is horizontal. I have. The casing 1 includes a motor case 2 described below,
The motor case 2 includes an oil tank 3 and a thrust receiver 4, and an electric motor 6 described below is built in the motor case 2.

Reference numeral 2 denotes a motor case of the casing 1. The motor case 2 has a substantially cylindrical tube portion 2A extending forward and rearward (horizontally), and a front cover portion provided on the front side of the tube portion 2A. And a rear cover 2C mounted on the rear side of the cylindrical portion 2A, and a bearing mounting portion 2D is formed at the center of the rear cover 2C. Further, a shaft insertion hole 2E through which a distal end side of a drive shaft 9 described later is inserted is provided at the front end of the front bearing mounting portion 2B.

Reference numeral 3 denotes an oil tank provided on the casing 1 at a lower side of the motor case 2. The oil tank 3 is formed as a box-shaped container including a part of a thrust receiver 4 described later. Contains an oil solution.

Reference numeral 4 denotes a casing 1, which is an annular thrust receiver provided on the front side of the motor case 2. The thrust receiver 4 is integrally mounted on the front side of the motor case 2 and the oil tank 3. An annular recess 4A is formed on the inner peripheral side of the thrust receiver 4 toward the front side, and a mirror plate 15A of the orbiting scroll 15 described later is disposed in the annular recess 4A. An annular sliding surface 4B is formed in the annular recess 4A of the thrust receiver 4 so as to slide on the end plate 15A. The sliding contact surface 4B applies a thrust load acting on the orbiting scroll 15 to the end plate 15A. It is configured to accept.

Reference numeral 5 denotes a fixed scroll provided on the front side of the thrust receiver 4 of the casing 1;
A fixed side member is formed together with the casing 1. Also,
The fixed scroll 5 has a substantially disk-shaped end plate 5A disposed so that the center thereof is coincident with an axis O1-O1 of a rotating shaft portion 10 of a drive shaft 9 described later, and is provided upright on the surface of the end plate 5A. A spiral wrap portion 5B, a cylindrical portion 5C axially protruding from the outer peripheral side of the end plate 5A so as to surround the wrap portion 5B, and a radially outward protruding portion from the outer peripheral side of the cylindrical portion 5C;
A flange portion 5D attached to the thrust receiver 4 in abutment.

Reference numeral 6 denotes an electric motor provided in the motor case 2 of the casing 1. The electric motor 6 is a stator 7 fixedly provided on the inner peripheral side of the cylindrical portion 2A of the motor case 2.
And a rotor 8 rotatably arranged on the inner peripheral side of the stator 7 and a drive shaft 9 described later. The rotor 8 is fixedly attached to the outer peripheral side of the drive shaft 9. I have. The electric motor 6 drives the drive shaft 9 by rotating the rotor 8 with respect to the stator 7 by external power supply.

Reference numeral 9 denotes a drive shaft constituting a part of the electric motor 6, and the drive shaft 9 drives the orbiting scroll 15 to orbit. The drive shaft 9 extends in the motor case 2 of the casing 1 in the axial direction (front and rear directions), and the eccentric shaft protrudes from the tip of the rotary shaft 10. It is constituted by a shaft portion 11.

First, the rotary shaft 10 has a large diameter portion 1 at the tip end.
0A, and the leading end of the large diameter portion 10A is a shaft end 10C via a step 10B as shown in FIG. The large-diameter portion 10A on the distal end side of the rotating shaft portion 10 is attached to the bearing attaching portion 2B of the motor case 2 via the ball bearing 12, and the proximal end portion is attached to the bearing attaching portion 2D via the ball bearing 13. As a result, it is possible to rotate around the axis O1-O1. When the drive shaft 9 is attached to the motor case 2, the shaft end 10C of the rotary shaft 10 projects forward from the shaft insertion hole 2E. Further, the shaft end 10
Reference character C is used to fit a rotation shaft fitting hole 25A of the balance weight 24, which will be described later, and has an outer diameter dimension D1.

On the other hand, the eccentric shaft portion 11 is located near the outer peripheral side of the shaft end portion 10C and is provided so as to protrude forward, and its axis O2-O2 has a dimension δ with respect to the axis O1-O1 of the rotary shaft portion 10.
Only one is eccentric. Further, the eccentric shaft portion 11 has an outer diameter dimension D2, and is rotatably connected to a boss portion 15C of the orbiting scroll 15 via the orbiting bearing 14.

Reference numeral 15 denotes an orbiting scroll provided on the drive shaft 9 in the casing 1 so as to be orbitable.
5 is an end plate 15A formed in a disk shape, and the end plate 15A
Spiral wrap 15 erected in the axial direction from the surface side of
And B. The end plate 15A of the orbiting scroll 15 has a boss 1 at the center on the back side.
An eccentric shaft 11 of a drive shaft 9 described later is rotatably attached to the boss 15C. The end surface of the end plate 15A is in sliding contact with the flange portion 5D of the fixed scroll 5, and the rear surface (back surface) is a sliding contact surface 15D in sliding contact with the thrust receiver 4.

The orbiting scroll 15 is disposed so as to overlap with the wrap portion 5B of the fixed scroll 5 by being shifted by, for example, 180 degrees.
A plurality of compression chambers 16, 16,... Are defined between 15B. During the operation of the scroll air compressor, the orbiting scroll 15 orbits the air while sucking air from a suction port (not shown) provided on the outer peripheral side of the fixed scroll 5 into the compression chamber 16 on the outer peripheral side. During the movement, the compressed air is sequentially compressed in each of the compression chambers 16, and finally the compressed air is discharged from the center compression chamber 16 to the outside through a discharge port 17 provided at the center of the fixed scroll 5.

Reference numeral 18 denotes the thrust receiver 4 and the orbiting scroll 15
The Oldham ring 18 is slidably provided between the rotating scroll 15 and the Oldham ring 18 slides in two axial directions orthogonal to each other on the back side of the orbiting scroll 15 when the orbiting scroll 15 makes a revolving motion. This is to prevent the orbiting scroll 15 from rotating.

Reference numeral 19 denotes an oil liquid supply device for supplying the oil liquid in the oil tank 3 to a portion requiring cooling and lubrication, for example, a sliding contact surface 4B of the thrust receiver 4, a swing bearing 14 described later, and the like. The device 19 is roughly constituted by a suction passage 20, an oil supply pump 22, and a discharge passage 23 to be described later.

Reference numeral 20 denotes a suction passage provided in the thrust receiver 4. The suction passage 20 has one end opening into the oil liquid in the oil tank 3 through the suction pipe 20A, and the other end inside the oil supply pump 22. Communicating. In the middle of the suction passage 20, there is provided a strainer 21 for catching foreign substances such as abrasion powder and debris mixed in the oil liquid.

Reference numeral 22 denotes a thrust receiver 4 and an orbiting scroll 15
And a refueling pump provided between the
Is described, for example, in Japanese Patent Application Laid-Open No. 2000-24 filed by the present applicant.
The oil pump is substantially similar to the oil supply pump described in Japanese Patent No. 9087, and is configured to move integrally with the orbiting scroll 15 to discharge the oil liquid in the oil tank 3 from the suction passage 20 to the discharge passage 23 described later. is there.

Reference numeral 23 denotes a discharge passage provided radially inside the end plate 15A of the orbiting scroll 15.
Has one end communicating with the oil supply pump 22 and the other end opening between the sliding contact surface 4B of the thrust receiver 4 and the sliding contact surface 15D of the orbiting scroll 15. A middle portion in the length direction of the discharge passage 23 is opened in the boss 15C of the orbiting scroll 15.

Numeral 24 is a balance weight fitted and mounted on the tip end side of the drive shaft 9.
Is to balance the rotation of the drive shaft 9 when the orbiting scroll 15 is turned. Further, the balance weight 24 is attached to an attachment cylinder 25 attached to the outer peripheral side of the drive shaft 9.
And a weight 26 extending radially outward from the mounting cylinder 25 in a fan shape.

As shown in FIGS. 2 and 3, the mounting cylinder 25 has a large-diameter rotary shaft fitting hole 25A opened on the rear side.
And a small-diameter eccentric shaft portion fitting hole 25C which is located near the outer periphery of the bottom 25B of the rotary shaft portion fitting hole 25A and penetrates the front surface.
And

Here, the rotary shaft portion fitting hole 2 of the mounting cylinder portion 25
5A is a shaft end 1 provided on a rotation shaft 10 of the drive shaft 9.
For example, when the outer diameter D1 of the shaft end 10C is φ30 mm and 0 to -13 μm (about h6), the inner diameter D3 of the rotary shaft fitting hole 25A is φ30 mm.
Is set to +7 to +20 μm (fitting of about G6), and the dimensions are such that rattling does not occur when fitted.

The eccentric shaft portion fitting hole 25C is
Of the eccentric shaft 11
When the outer diameter D2 of the eccentric shaft portion fitting hole 25C is φ18 mm, the inner diameter D4 of the eccentric shaft portion fitting hole 25C is set to +6 to +17 μm (about G6) when the outer diameter D2 of φ18 mm is Similar to the fitting hole 25A, the size is such that rattling does not occur when fitted.

Further, the axis O3 of the rotation shaft fitting hole 25A is formed.
The eccentric dimension δ2 of the axis O4-O4 of the eccentric shaft part fitting hole 25C with respect to -O3 is equal to the eccentric dimension δ1 of the axis O2-O2 of the eccentric shaft part 11 with respect to the axis O1-O1 of the rotary shaft part 10, for example, about 10 μm. Set to the error range.

As described above, the shaft end 10C of the rotating shaft 10
Of Rotation Shaft Fitting Hole 25A with Eccentric Shaft 1
The fitting of the eccentric shaft portion fitting hole 25C to the eccentric shaft part 1 is about G6, and the error of the eccentric dimension δ2 to the eccentric dimension δ1 is 10 μm.
The balance weight 2
4 is that the mounting cylinder portion 25 is mounted from the tip end side of the drive shaft 9, thereby using the eccentrically disposed rotating shaft portion 10 and the eccentric shaft portion 11 to cause rattling in the rotation direction. Instead, it can be fitted in a regular position.

A return passage 27 is provided between the eccentric shaft portion 11 of the drive shaft 9 and the mounting cylinder portion 25 of the balance weight 24. The return passage 27 extends from the oil supply pump 22 to the boss portion of the orbiting scroll 15. A part of the oil liquid discharged into 15C is discharged into the casing 1 and returned into the oil tank 3.

The scroll type air compressor according to the present embodiment has the above-described configuration. Next, the compression operation will be described.

First, when the drive shaft 9 is rotated by the electric motor 6, the orbiting scroll 15 performs a circular motion (orbiting motion) having a constant orbiting radius around the drive shaft 9, and the wrap portion 5B of the fixed scroll 5 Compression chambers 16, 16, 16.
... is continuously reduced. Thereby, the fixed scroll 5
The outside air sucked from the suction port of the fixed scroll 5 is sequentially compressed in each of the compression chambers 16, and the compressed air is
From 7 is stored in an external air tank or the like.

The balance weight 24 is positioned so that the weight portion 26 is positioned on the opposite side of the eccentric shaft portion 11 with respect to the rotary shaft portion 10 in the eccentric direction. A predetermined load can be applied, and the rotation of the drive shaft 9 can be balanced.

As described above, according to the present embodiment, the drive shaft 9 and the balance weight 24 are separately provided, and the rotary shaft 10 and the eccentric shaft 11 of the drive shaft 9 which are eccentrically disposed are provided. The balance weight 24 is attached to the drive shaft 9 in a non-rotating state by fitting the rotation shaft fitting hole 25A and the eccentric shaft fitting hole 25C of the balance weight 24. As a result, the balance weight 24 can be attached to the mounting cylinder 25 only from the front end of the drive shaft 9 by using a separate screw,
Without using a key or the like, it can be easily attached to the drive shaft 9 in a detented state.

As a result, the balance weight 24 can be mounted in a non-rotating state only by fitting to the drive shaft 9, so that components such as screws and keys can be eliminated.
Also, machining of screw holes, key grooves, and the like can be omitted, so that assembling workability can be improved, manufacturing costs can be reduced, and the like.

Next, FIGS. 4 and 5 show a second embodiment of the present invention. A feature of the present embodiment is that a gap is formed between the rotating shaft portion and the rotating shaft portion fitting hole, and an elastic ring is provided in the gap. Note that, in the present embodiment, the same components as those in the above-described first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

A balance weight 31 according to the present embodiment is used in place of the balance weight 24 according to the first embodiment. The balance weight 31 is substantially the same as the balance weight 24 according to the first embodiment. And a mounting portion 32 attached to the outer peripheral side of the drive shaft 9, and a weight portion 33 extending from the mounting portion 32 radially outward in a fan shape. However, in the balance weight 31 according to the present embodiment, a rotating shaft portion fitting hole 32A described later provided in the mounting cylinder portion 32 is formed larger than a shaft end portion 10C provided in the rotating shaft portion 10 of the drive shaft 9. This is different from the balance weight 24 according to the first embodiment.

The mounting cylindrical portion 32 has a large-diameter rotary shaft fitting hole 32A opened on the rear surface side and the rotary shaft fitting hole 3A.
And a small-diameter eccentric shaft fitting hole 32C which is located near the outer peripheral side of the hole bottom 32B of the 2A and penetrates the front surface, and an elastic ring 34 described later is provided on the opening end side of the rotating shaft fitting hole 32A.
Is formed to form a chamfer 32D.

Here, the rotary shaft portion fitting hole 3 of the mounting cylinder portion 32
2A is an outer diameter D1 of the shaft end 10C as shown in FIG.
The outer diameter D5 is set to be larger than the outer diameter D5 by the gap G. The gap G is set to a size sufficient to allow a machining error in the inner diameter dimension when the rotary shaft portion fitting hole 32A and the eccentric shaft portion fitting hole 32C are machined, a misalignment, and the like.

Similarly to the eccentric shaft portion fitting hole 25C according to the first embodiment, the eccentric shaft portion fitting hole 32C has, for example, an outer diameter D2 of the eccentric shaft portion 11 of φ18 mm and 0 to -11.
In the case of μm (about h6), the inner diameter dimension D6 of the eccentric shaft portion fitting hole 32C is set to +6 to +17 μm (about G6) at φ18 mm, which is a dimension that does not cause rattling when fitted. ing.

As described above, in the balance weight 31 according to the present embodiment, although the fitting of the eccentric shaft portion fitting hole 32C with the eccentric shaft portion 11 is set to about G6, the shaft end portion 10C of the rotating shaft portion 10 is formed. Rotation shaft portion fitting hole 32
Since A is formed to be larger by the gap G, the mounting cylinder 32 can be assembled to the drive shaft 9 even when the accuracy of the inner diameter and eccentricity of the rotary shaft fitting hole 32A is set low.

Numeral 34 denotes an elastic ring provided between the rotary shaft 10 of the drive shaft 9 and the mounting cylinder 32 of the balance weight 31. The elastic ring 34 is made of an elastic rubber material and has a circular cross section. Is formed as an annular body. When the balance weight 31 is mounted on the drive shaft 9, the elastic ring 34 is provided with a chamfered portion 32 </ b> D of the mounting cylindrical portion 32.
And the step portion 10B of the rotary shaft portion 10 and the outer peripheral surface of the shaft end portion 10C. Thereby, the elastic ring 34 supports the balance weight 31 on the drive shaft 9 in a state where it is prevented from rotating while allowing a processing error in the inner diameter of the eccentric shaft portion fitting hole 32C, misalignment, and the like.

Thus, according to the present embodiment, the rotary shaft portion fitting hole 32A is formed to be larger than the shaft end portion 10C of the rotary shaft portion 10 by the gap G.
Even when the accuracy of the inner diameter dimension and the eccentric dimension of 2A is set to be low, the processing error and the misalignment at this time can be allowed, and the mounting cylinder 32 can be assembled to the drive shaft 9.
In addition, the balance weight 31 can be supported on the drive shaft 9 in a detented state while processing errors, misalignment, and the like are allowed by the elastic ring 34. As a result, the accuracy in processing the balance weight 31 can be set low, and the manufacturing cost can be reduced.

The rotary shaft portion fitting hole 32 of the mounting cylinder portion 32
A is fitted to the shaft end 10C of the rotating shaft 10 with a gap G, and the eccentric shaft fitting hole 32C is fitted to the eccentric shaft 11 with a fitting of about G6. 32
The space between C and the eccentric shaft 11 can be maintained almost liquid-tight. Thereby, it is possible to prevent the oil liquid flowing through the return passage 27 provided between the eccentric shaft portion 11 and the mounting cylinder portion 32 from leaking from the middle of the return passage 27.

In the second embodiment, the case where the elastic ring 34 is formed as an annular body having a circular cross section has been described as an example. However, the present invention is not limited to this. Alternatively, another elastic ring having a polygonal shape may be used.

Further, in each embodiment, the scroll type air compressor in which the electric motor 6 is built in the casing 1 has been described as an example. However, the present invention is not limited to this. For example, the drive shaft may be driven by an external power source. May be applied to a scroll-type air compressor of a type that rotationally drives.

Further, in each embodiment, the case where the present invention is applied to an oil supply type scroll type air compressor having an oil tank 3 has been described as an example. However, the present invention is not limited to this, and the oil supply type scroll type air compressor is not limited to this. It may be applied to a type air compressor.

Furthermore, in each of the embodiments, a scroll 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. be able to.

[0053]

As described above in detail, according to the first aspect of the present invention, the fitting hole of the balance weight fitted to the drive shaft is fitted to the rotating shaft portion fitted to the rotating shaft portion of the drive shaft. It is constituted by a hole and an eccentric shaft portion fitting hole fitted to the eccentric shaft portion. Therefore, when the rotating shaft portion fitting hole is fitted to the rotating shaft portion of the drive shaft and the eccentric shaft portion fitting hole is fitted to the eccentric shaft portion, the two eccentric shaft portions and the fitting hole fit together. The balance weight can be attached to the drive shaft in a non-rotating state.

As a result, since the balance weight can be easily attached simply by fitting it to the drive shaft, parts such as screws and keys used in the prior art can be eliminated, and the assembly workability can be improved. In addition, the manufacturing cost can be reduced.

[Brief description of the drawings]

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

FIG. 2 is an enlarged longitudinal sectional view showing a main part of the drive shaft and balance weight in FIG. 1 in an enlarged manner.

FIG. 3 is an exploded perspective view showing the drive shaft and the balance weight in an exploded state.

FIG. 4 is an enlarged longitudinal sectional view of a main part showing a balance weight and an elastic ring together with a drive shaft according to a second embodiment of the present invention.

FIG. 5 is an enlarged longitudinal sectional view of a main part showing the balance weight, elastic ring, and drive shaft in FIG. 4 in an enlarged manner.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Casing (fixed side member) 5 Fixed scroll (fixed side member) 9 Drive shaft 10 Rotating shaft part 10C Shaft end part 11 Eccentric shaft part 15 Orbiting scroll 16 Compression chamber 24, 31 Balance weight 25, 32 Mounting cylinder part 25A, 32A Rotating shaft part fitting hole 25C, 32C Eccentric shaft part fitting hole 26, 33 Weight part O1-O1 Rotary shaft part axis O2-O2 Eccentric shaft part axis O3-O3 Rotation shaft part fitting hole O4-O4 Axis line of eccentric shaft part fitting hole δ1, δ2 Eccentric dimension D1 Outer diameter dimension of shaft end part D2 Outer diameter dimension of eccentric shaft part D3, D5 Inner diameter dimension of rotating shaft part fitting hole D4, D6 Eccentric shaft part fitting hole Bore size of

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masanori Sugimoto 1116 Koizono, Ayase-shi, Kanagawa Prefecture Tokiko Corporation Sagami Plant (72) Inventor Yoshio Kobayashi 1116 Koizono, Ayase-shi, Kanagawa Prefecture Tokiko Corporation Sagami Plant F-term ( Reference) 3H039 AA04 AA12 BB07 BB08 CC13 CC20

Claims (1)

[Claims] 1. A fixed side member comprising a casing and a fixed scroll provided in the casing, a rotating shaft portion rotatably provided in the casing, and eccentrically provided on a tip end side of the rotating shaft portion. A drive shaft comprising an eccentric shaft portion, a orbiting scroll provided on the eccentric shaft portion of the drive shaft so as to be rotatable, and defining a plurality of compression chambers between the drive shaft and the fixed scroll; And a balance weight that is provided to be fitted and that balances the rotation of the drive shaft when the orbiting scroll is turned. The fitting hole of the balance weight is provided with a rotating shaft of the drive shaft. A scroll type fluid machine comprising: a rotary shaft portion fitting hole fitted to a portion; and an eccentric shaft portion fitting hole fitted to the eccentric shaft portion.