JP2000297768A - Scroll compressor - Google Patents

Abstract

(57) [Summary] [PROBLEMS] In a scroll compressor, the degree of freedom in design of a crank part is widened, strength is secured, and high-precision relative positioning between an orbiting scroll and a fixed scroll is realized to achieve high efficiency. And high reliability. A flange portion (3d) larger than the outer diameter of a drive shaft (3) is provided between a crank portion (3a) and a drive shaft (3), and a boss end surface (1e) of a crank bearing (1d) is used for relative positioning of a fixed scroll (2) and an orbiting scroll (1). However, a gap is provided so as to always stably contact the flange end face 3c on the crank side. According to the above configuration, the strength of the crank portion 3a is increased, and the relative positioning of both scrolls with high accuracy and stability is possible.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor.

[0002]

2. Description of the Related Art Conventionally, this kind of technology is disclosed in
There is one described in JP-A-231186. This will be described below with reference to the drawings.

The structure of a conventional hermetic scroll compressor, as shown in FIG. 4, is a scroll compressor comprising a orbiting scroll 1 and a fixed scroll 2, which perform a relatively orbiting motion, a drive shaft 3 having a crank portion 3a, and a frame 4. It comprises a machine, a motor 5 for driving the machine, and a sealed container 6 for housing these. The orbiting scroll 1 has a spiral wrap 1b on a head plate 1a, a rotation preventing mechanism 1c for preventing rotation and a crank bearing 1d into which a crank portion 3a of a drive shaft 3 is inserted, and fixed on the back. The scroll 2 also has a wrap 2b on the end plate 2a.

[0004] The fixed scroll 2 and the orbiting scroll 1
The wraps 2a and 1a are combined with the wraps 2a and 1a facing inward. In general, regarding this assembling, in order to improve the assembling property, in many cases, the relative positions are determined by using a positioning reference hole or the like, and the assembling is often performed.

[0005] The combined two scrolls relatively rotate by the rotation of the motor 5 by the action of the crank part 3a of the drive shaft 3 and the rotation preventing mechanism 1c, and the wraps 1b, 2b of the two scrolls and the end plate 1a. , As the space formed in 2a moves to the center, its volume decreases,
As a result, the inhaled gas is compressed and discharged.

[0006] Between the orbiting scroll 1 and the fixed scroll 2, a force for separating the two scrolls is applied by the pressure of the gas. To prevent this, the orbiting scroll 1
The pressure in the intermediate pressure chamber 7 formed by the end plate 1a and the frame 4 is maintained at a pressure intermediate between the suction pressure and the discharge pressure.

The drive shaft 3 is provided with an oil supply hole 3b for supplying lubricating oil at the lower portion of the closed container 6 to each sliding portion. The oil supplied to the crank bearing 1d of the orbiting scroll 1 flows out to the intermediate chamber 7 via the bearing.

In order to prevent an increase in mechanical loss and abrasion when the end face 3c of the boss and the end face 1e of the boss come into contact with each other, the drive shaft 3 is provided outside the boss 3a so that a thrust force to the orbiting scroll side is not generated. The outer diameter of the drive shaft 3 is equal to or less than the diameter. In addition, the balance weight 8 is often attached to the flange portion 3d, and the outer diameter of the collar portion 3d is not configured to be large due to a problem that the balance weight 8 becomes large. Therefore, when the thrust force to the orbiting scroll 1 side is generated for some reason, the flange end face 3
In some cases, the outer diameter portion c rotates across the boss end face 1c. In order to solve such a problem, the thrust bearing member 9 and the like are fitted and attached to the flange 3d.

[0009]

However, in the above-mentioned conventional construction, when the amount of eccentricity of the crank portion 3a is to be increased, the outer diameter of the collar portion 3d is small.
The outer diameter of a cannot be made large. Therefore, since the strength of the crank portion 3a is significantly reduced, there is a problem that the drive shaft 3 and the crank portion 3a cannot be reduced in size and the scroll compressor becomes larger.

In order to reduce the leakage loss between the wraps 1b and 2b and to improve the efficiency, the fixed scroll 2 and the orbiting scroll 1 are not used for positioning using a reference hole or the like.
Requires high-precision relative positioning. In order to realize this, it is necessary to employ a technique of relatively moving the two scrolls while rotating the drive shaft 3 and measuring the gap between the wraps 1b and 2b with high accuracy. In a normal case, it is effective that the positioning is performed with the end plate 2a surface of the fixed scroll 2 facing downward. However, in the above-described conventional configuration, the boss end face 1e is opposed to the flange end face 3e.
High accuracy measurement between the lap gaps is not possible because the contact between the lap gaps is limited due to the lack of stability and accuracy due to the partial contact of c, and the loss of thrust surface accuracy when a thrust bearing member is fitted. There was such a problem.

An object of the present invention is to solve such a conventional problem and to provide a highly reliable and efficient scroll compressor.

[0012]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a collar portion between a crank portion and a drive shaft which is larger than an outer diameter of a drive shaft, and is used when positioning a fixed and orbiting scroll relatively. A gap is formed so that the end surface of the boss portion is always stably in contact with the end surface of the flange portion on the crank portion side. According to the above configuration, the strength of the crank portion is increased, and the relative positioning of both scrolls can be performed stably and with high accuracy.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The first embodiment has a collar portion larger than the outer diameter of the drive shaft between the crank portion and the drive shaft, and the boss portion into which the crank portion is inserted always has the outer diameter of the collar portion. An axial gap A is provided between the end face of the flange part on the crank part side and the end face of the boss part, and an axial gap B is provided between the end face of the crank part and the bottom of the crank bearing. This is a configuration having a great relationship with A. This makes it possible to secure the amount of eccentricity even when the outer diameter of the crank portion is increased, thereby increasing the degree of freedom in design and securing the strength in the crank portion. Also, at the time of the relative positioning of the fixed and orbiting scrolls, the end face of the collar part can always contact the end face of the boss part.

In the second embodiment, a flat portion perpendicular to the crank portion is provided on the end surface of the flange portion, and a surface parallel to the end surface of the orbiting scroll is provided on the end surface of the boss portion. As a result, at the time of relative positioning of the fixed and orbiting scrolls, the end faces of the flanges are in contact with the end faces of the bosses, and the crank portion is positioned perpendicular to the end surface of the orbiting scroll.

In the third embodiment, one or both of the end face of the flange and the flat face of the end face of the boss of the crank bearing are finished by polishing. As a result, the surface accuracy in the flat portion is improved, and the flange end surface can stably and accurately contact the boss end surface.

According to a fourth embodiment, in the scroll compressor according to the first to third embodiments, the orbiting scroll and the fixed scroll are relatively moved in a state where the end surface of the boss portion and the end surface of the flange portion on the crank portion side are in contact with each other. The two scrolls are moved relative to each other to perform relative positioning, and the gap between the wraps of the two scrolls can be stably measured with high accuracy and assembled.

[0017]

An embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional view of one embodiment of the scroll compressor of the present invention, and FIG. 2 is an enlarged view of a main part. A scroll compressor according to one embodiment of the present invention includes a orbiting scroll 1 and a fixed scroll 2 which relatively perform orbiting motion, and a crank portion 3a.
, A scroll compressor including a drive shaft 3 and a frame 4, a motor 5 for driving the scroll compressor, and a sealed container 6 for accommodating the scroll compressor. The orbiting scroll 1 has a spiral wrap 1b on a head plate 1a, a rotation preventing mechanism 1c for preventing rotation and a crank bearing 1d into which a crank portion 3a of a drive shaft 3 is inserted, and fixed on the back. The scroll 2 also has a wrap 2b on the end plate 2a.

The fixed scroll 2 and the orbiting scroll 1
The wraps 2b and 1b are combined with the wraps 2b and 1b facing inward. Generally, in order to improve the assemblability, in many cases, the relative positions of the scrolls are determined by using a positioning reference hole or the like, but in this embodiment, the relative positions of the two scrolls are accurately determined. Positioning is being performed.

The combined two scrolls relatively rotate by the rotation of the motor 5 by the action of the crank part 3a of the drive shaft 3 and the rotation preventing mechanism 1c, and the wraps 1b, 2b of the two scrolls and the end plate 1a. , As the space formed in 2a moves to the center, its volume decreases,
As a result, the inhaled gas is compressed. After the compressed gas is discharged into the closed container 6, the compressed gas is discharged from the closed container 6.

Between the orbiting scroll 1 and the fixed scroll 2, a force for separating the two scrolls is applied by the pressure of the gas. To prevent this, the orbiting scroll 1
The pressure in the intermediate pressure chamber 7 formed by the end plate 1a and the frame 4 is maintained at a pressure intermediate between the suction pressure and the discharge pressure.

The drive shaft 3 is provided with a lubrication hole 3b for supplying lubricating oil at the lower part of the sealed container 6 to each sliding portion. The oil supplied to the crank bearing 1d of the orbiting scroll 1 flows out to the intermediate chamber 7.

The end face 3c of the flange of the drive shaft 3 and the end face 1 of the boss
When e contacts, increase in mechanical loss, wear, etc. occur. In order to prevent this, the orbiting scroll 1
The outer diameter of the drive shaft 3 is equal to or less than the outer diameter of the crank portion 3a so that a thrust force due to a pressure difference to the side is not generated. The thrust force of the drive shaft 3 toward the opposite side of the crank portion is received by a drive shaft thrust receiver 3e also serving as a bearing.

A flange 3d larger than the outer diameter of the drive shaft 3 is provided between the drive shaft 3 and the crank 3a, and an axial gap 9 is provided between the flange end face 3c on the crank 3a side and the boss 1f.
An axial gap 10 is provided between the end face 3f of the crank part and the bottom of the crank bearing 1d. In addition, the axial gap 1
0 is larger than the axial gap 9. Therefore, even when a thrust force is generated on the drive shaft 3 on the side of the crank portion 3a, the flange end surface 3c and the boss end surface 1e of the crank bearing 1d always contact before the crank end surface 3f contacts the bottom of the crank bearing 1d.

The boss portion 1f is configured to always be located inside the outer diameter end of the collar portion 3d regardless of the direction in which the crank portion 3a rotates.

In the above configuration, even when the amount of eccentricity of the crank portion 3a is large, the outer diameter of the crank portion 3a can be made large, the strength can be secured, and the drive shaft 3 and the crank portion 3a can be downsized. It is. When the thrust force to the orbiting scroll 1 is generated for some reason, the outer diameter of the flange end face 3c does not rotate across the boss end face 1e. A stable contact with the end face 3c. Therefore, mechanical loss can be minimized. Further, even when an excessive acceleration of the drive shaft 3 toward the orbiting scroll 1 occurs due to a drop or the like, the end plate 1 on which the wrap 1b stands upright.
Since the impact load is not directly applied to “a”, the deformation of the end plate 1a, which is a factor of performance degradation, can be suppressed.

When considering the efficiency of the scroll compressor, the wrap 1 of the orbiting scroll 1 and the fixed scroll 2 is considered.
It is necessary to reduce the leakage loss between b and 2b. For that purpose, the relative positioning of both scrolls must be performed with high precision. An example of this high-precision relative positioning will be described below.

FIG. 3 shows the outline. The fixed scroll 2 is installed on the movable horizontal surface 10 with the end plate 2 a surface of the fixed scroll 2 facing downward, and is fixed by the fixed portion clamp 11 and the movable portion clamp 12. At this time, in the case of the structure described in claim 1, as described above, the flange end face 3c necessarily contacts the boss end face 1e. In this state, while rotating the drive shaft 3 in each direction, the orbiting scroll 1 and the fixed scroll 2 are relatively moved, and the gap between the wraps 1b and 2b in each direction is measured. The ideal relative position of both scrolls is determined from the measured gap and fixed.

According to this method, the gap between the wraps 1b and 2b can be optimized, and the leakage loss of the compressed gas in the actual operating state of the scroll compressor can be reduced.

The following are examples of stably measuring the gap between the wraps 1b and 2b with high accuracy. In FIG. 1, a flat portion perpendicular to the crank portion 3a is provided on a flange end surface 3c, and an end plate 1a of the orbiting scroll 1 is provided.
The flat part parallel to the boss end face 1e of the crank bearing 1d
There is something to provide. With this configuration, the crank portion 3a is correctly positioned perpendicular to the end plate 1a of the orbiting scroll 1, so that the gap between the wraps 1b and 2b can be measured with higher accuracy. As a result, more accurate relative positioning of both scrolls can be performed.

If one or both of the flat surface of the flange end face 3c and the boss end face 1e is finished by polishing, the surface roughness is 0.001 mm and the parallelism is 0.005 mm.
mm and a squareness of about 0.005 mm, the gap between the wraps 1b and 2b can be measured at the 0.001 mm level, and the relative positioning of the two scrolls in a more ideal state can be achieved. Further, even if the flange end face 3c of the drive shaft 3 comes into contact with the boss end face 1e of the crank bearing 1d for any reason, the high-precision and wide flat portion acts as a thrust bearing to increase mechanical loss and wear. Can be prevented.

[0032]

As is apparent from the above embodiment, even if the drive shaft and the crank portion are downsized, the strength can be secured, the reliability can be improved, and the scroll compressor can be downsized. Further, even if an unexpected situation such as a drop occurs, it is possible to suppress the deformation of the head plate due to the performance degradation.

Furthermore, since the relative positioning between the fixed scroll and the orbiting scroll can be realized with high precision, the leakage loss between the wraps can be reduced, and the efficiency of the scroll compressor can be increased.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll compressor showing one embodiment of the present invention.

FIG. 2 is an enlarged view of a main part of FIG. 1;

FIG. 3 is a diagram showing an embodiment of relative positioning of a scroll.

FIG. 4 is a longitudinal sectional view of a conventional scroll compressor.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 orbiting scroll 1a end plate 1b lap 1c anti-rotation mechanism 1d crank bearing 1e boss end face 1f boss 2 fixed scroll 2a end plate 2b lap 3 drive shaft 3a crank portion 3b lubrication hole 3c collar end face 3d collar bearing 3e Crank part end face 4 Frame 5 Motor 6 Closed vessel 7 Intermediate chamber 8 Balance weight 9 Thrust bearing member 10 Movable horizontal plane 11 Fixed part clamp 12 Movable part clamp

Continued on the front page (72) Inventor Noboru Iida 1006 Kazuma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Inventor Hiroyuki Kawano 1006 Okadoma Kadoma, Kadoma City Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Invention Person Hiromasa Ashiya 1006 Kadoma Kadoma, Kadoma City, Osaka Prefecture (72) Inventor Shuichi Yamamoto 1006 Kadoma Kadoma, Kadoma City, Osaka Prefecture Inside the Matsushita Electric Industrial Co., Ltd. (72) Kiyoshi Sawai Kaoru Kadoma, Osaka Prefecture 1006 Kadoma Matsushita Electric Industrial Co., Ltd. F term (reference) 3H039 AA03 AA06 AA12 BB05 BB28 CC12 CC13 CC36

Claims (4)

[Claims] An orbiting scroll and a fixed scroll comprising a head plate, a spiral wrap standing upright on the head plate, a drive shaft having a crank portion for giving a turning motion to the orbiting scroll, and the wrap of the orbiting scroll A crank bearing in which the crank portion is rotatably fitted to the rear surface of the end plate on the opposite side, a rotation preventing mechanism of the orbiting scroll, and the wraps of both scrolls are combined inwardly toward each other, and each of the wraps is A scroll compressor in which the two scrolls perform relative movement so that the volume formed by the end plate moves toward the center of the scroll so that the volume of the scroll decreases, and the drive is provided between the crank portion and the drive shaft. It has a flange portion larger than the shaft outer diameter, and the boss portion into which the crank portion is inserted is always inside the flange portion outer diameter end. An axial gap A between the flange end face and the boss end face on the crank side, and an axial gap B between the crank end face and the crank bearing bottom, and the axial gap B is A scroll compressor, wherein the width of the scroll compressor is larger than the gap A in the axial direction. 2. A flat portion perpendicular to the crank portion is provided on an end surface of the flange portion on the crank portion side, and a flat portion parallel to the end plate surface of the orbiting scroll is provided on an end surface of the boss portion. 2. The scroll compressor according to 1. 3. The scroll compressor according to claim 2, wherein one or both of a flat portion of the end surface of the flange portion and a flat portion of the end surface of the boss portion on the crank portion side are finished by polishing. 4. The scroll compressor according to claim 1, wherein the orbiting scroll and the fixed scroll are combined with the end surface of the boss portion and the end surface of the flange portion on the crank portion side in contact with each other. A method of assembling a scroll compressor that relatively moves, positions, and fixes.