KR0133257B1 - Scroll type compressor - Google Patents

Abstract

In order to reduce the number of idle position regulating holes requiring high machining accuracy, to reduce the number of parts, and to improve the assemblability, the turning ring 9 is interposed between the hydraulic wall 2a and the scroll substrate 7a. The rotating element 9 is fixedly attached to the turning ring 9. The hydraulic plate 13 is joined to the hydraulic wall 2a by fitting between the fitting projection 13a and the fitting recess 2b. The element 10 for preventing rotation is inserted into the revolving position regulating holes 7c and 13b on the scroll substrate 7a and the hydraulic wall plate 13. The compression reaction force in the compression chamber 7 between the fixed scroll 1 and the movable scroll 7 can be transmitted to the hydraulic plate 13 through the hydraulic protrusions 9A and 9B formed on both sides of the turning ring 9. .

Description

Scroll compressor

1 is a side cross-sectional view of the entire compressor of one embodiment embodying the present invention.

2 is a cross-sectional view taken along line A-A of FIG.

3 is a longitudinal sectional view showing a state in which the movable scroll is idled by 180 ° in the state of FIG.

4 is an exploded perspective view.

5 is an exploded perspective view showing another example.

* Explanation of symbols for main parts of the drawings

1: Fixed scroll 2a: Hydraulic wall

2b: fitting recess 3: rotation axis

4: eccentric shaft 7: movable scroll

7a: scroll board 7c: idle position regulation hole

9: Slewing ring 9A, 9B: Hydraulic projection

10 element for preventing rotation 13 hydraulic plate

13b: idle position control hole

Industrial use

The present invention relates to a scroll compressor that forms a compression chamber that decreases in volume according to the revolution of the movable scroll between the fixed scroll and the movable scroll which is non-rotating and capable of revolving against the fixed scroll.

Conventional technology

As a scroll revolving mechanism of a scroll compressor, it is known from Japanese Patent Laid-Open No. 59-28082. In this revolving mechanism, a fixing ring and a movable amount are fixedly attached to each other by a race on both opposing surfaces of the housing accommodating the movable scroll and the movable scroll, and a plurality of pockets are opposed to each other and are permeately installed between the opposing pockets. The cylindrical bearing element is inserted. Cylindrical bearing elements are sandwiched between the peripheral walls of the opposing pockets and are driven. By this narrowing movement, the movable scroll stops rotation and revolves.

Challenges to the Invention

There is a relationship of D = d + r between the diameter d of the cylindrical bearing element, the diameter D of the pocket, and the idle radius r for forming the rotation restraint, and the diameter d of the cylindrical bearing element is determined by the idle radius r and the diameter D of the pocket. Regulated. The cylindrical bearing element transmits a compression reaction force acting on the movable scroll to the housing, and the housing receives the compression reaction force through the cylindrical bearing element. With such a hydraulic pressure function, the diameter d of the cylindrical bearing element can be enlarged by increasing the diameter D of the pocket.

However, an increase in the width of the stationary ring and the movable ring causes an enlargement of the body diameter of the compressor, and the compressor becomes larger. Sharing the required hydraulic pressure area with a plurality of cylindrical bearing elements in order to avoid the enlargement of the compressor and to receive the compression reaction force has to increase the number of cylindrical bearing elements. This increase in the number of cylindrical bearing elements leads to an increase in the number of pockets, but an increase in the number of pockets requiring high machining accuracy leads to an increase in machining time and cost.

A fixed race is bonded to the housing facing the movable scroll, and a movable race is bonded to the scroll substrate of the movable scroll. The cross section of the cylindrical bearing element is in sliding contact with these races. By interposing such a race, the housing and the movable scroll can be made of aluminum, which lacks abrasion resistance, and the compressor can be reduced in weight.

In both of the fixed race and the movable race bringing these advantages, a plurality of pins are pressed into the housing and the scroll substrate to stop rotation. However, in press-fitting a pin, it is necessary to set an exact size relationship between the pin diameter and the press-in groove diameter, and the press-in operation itself is difficult.

The present invention provides a scroll compressor that can reduce the number of pockets of a conventional apparatus, and furthermore, reduce the number of parts and improve assembly workability.

In order to solve the problem, according to the present invention, the hydraulic ring which receives the compression reaction force in the compression chamber acting on the movable scroll and the scroll substrate of the movable scroll are interposed therebetween, and both surfaces of the swing ring are respectively provided. A rotation preventing element to be fixedly attached, a hydraulic plate is provided at least on one side between the hydraulic wall and the pivot ring, and between the scroll substrate and the pivot ring, and a fitting protrusion is provided on the hydraulic plate. A fitting recess is provided on the joining target side of the hydraulic plate, the fitting projection is fitted to the fitting recess to join the hydraulic plate to at least one of the hydraulic wall and the scroll substrate, and the scroll substrate side and the hydraulic side wall are respectively A plurality of idle position regulating holes are arranged in the circumferential direction, and the idle position regulating holes of the hydraulic side wall Is inserted into the rotation blocking element on one side of the revolving ring, penetrates the rotation blocking element on the other side of the revolving ring through the rotational position restriction hole on the scroll substrate side, and the compression in the compression chamber acting on the movable scroll. A hydraulic element for transmitting the reaction force is interposed between the scroll substrate and the hydraulic wall.

Action

Accompanying the revolution of the movable scroll, the element for preventing rotation is in sliding contact along the peripheral surface of the idle position regulating hole. The swing ring is biased from the idle center side to the idle position of the movable scroll by this sliding contact action, and the contact position of the rotation preventing element with respect to the idle position regulating hole on the hydraulic wall side is the idle position of the rotation preventing element and the movable scroll side. The opposite side of the contact with the peripheral surface of the regulation hole is 180 degrees. This contact relationship prevents rotation of the movable scroll.

The hydraulic element is in sliding contact with the hydraulic plate. The sliding contact attempts to follow the turning of the hydraulic block by the sliding contact, but the fitting between the fitting recess and the fitting protrusion prevents the following turning.

Example

Hereinafter, the embodiment which actualized this invention is described based on FIG. 1 thru | or FIG.

As shown in FIG. 1, the aluminum front housing 2 is joined and fixed to the aluminum fixed scroll 1 which also serves as a rear housing. The rotary shaft 3 is rotatably supported in the front housing 2, and the eccentric shaft 4 is fixedly attached to the rotary shaft 3.

The balance weight 5 and the bush 6 are rotatably supported by the eccentric shaft 4. The bush 6 is rotatably supported by the radial bearing 8 so that the movable scroll 7 is opposed to the fixed scroll 1, and the scroll substrates 1a and 7a of both scrolls 1 and 7 and The compression chamber p is formed by the vortex walls 1b and 7b.

An aluminum turning ring 9 is interposed between the scroll substrate 7a of the movable scroll 7 and the hydraulic wall 2a of the front housing 2. On one surface of the turning ring 9, a plurality of hydraulic projections 9A are arranged in the circumferential direction. The same number of hydraulic projections 9B are also arranged in the circumferential direction on the other side of the turning ring 9. The hydraulic projection 9A and the hydraulic projection 9B are arranged at the same interval angle position toward the rear side. A circumferential rotation preventing element 910 is penetrated and fixed to the turning ring 9. The element 10 for preventing rotation is arranged at angular intervals between the arrangements of the hydraulic projections 9A and 9B.

An annular hydraulic plate 13 made of iron is interposed between the hydraulic wall 2a and the turning ring 9. A plurality of engaging projections 13a are bent on the inner circumferential surface of the hydraulic plate 13. A plurality of fitting recesses 2b are cut off from the inner circumferential end of the pressure receiving wall 2a. By fitting the fitting projection 13a to the fitting recess 2b, the hydraulic plate 13 is engaged with the hydraulic wall 2a in an unmovable manner.

In the hydraulic plate 13, the same number of revolving position regulating holes 13a as the rotation blocking element 10 are arranged in the circumferential direction. In the scroll substrate 7a, the same number of revolving position regulating holes 7c as in the rotating element 10 are arranged in the circumferential direction. All of the idle position regulating holes 13a and 7c are arranged at equal interval angle positions. End portions of the rotation blocking element 10 are inserted into the idle position regulating holes 13a and 7c. The protruding height of the cross section of the element for blocking rotation 10 at the front end surfaces of the hydraulic protrusions 9A and 9B does not contact the bottom faces of the idle position regulating holes 13a and 7c.

In accordance with the rotation of the eccentric shaft 4, the movable scroll 7 revolves around the rotation shaft 3, and the refrigerant gas introduced from the inlet (not shown) is compressed in the compression chamber P between the two scrolls 1,7. Flows into. The compression chamber P is made by converging toward the start end of the vortex walls 1b and 7b of both scrolls 1 and 7 with volume reduction according to the revolution of the movable scroll 7. The refrigerant gas compressed by the volume reduction of the compression chamber P is discharged into the discharge chamber 11 from the discharge port 1c on the scroll substrate 1a. The discharge port 1c is closed to be opened by the discharge valve 12 at the discharge chamber 11 side.

The compression reaction in the compression chamber P can be received by the hydraulic plate 13 through the scroll substrate 7a and the hydraulic projections 9B and 9A. That is, the hydraulic pressure protrusion 9B is in sliding contact, and the hydraulic pressure protrusion 9A is in sliding contact with the hydraulic plate 13. The surface of the scroll substrate 7a of the movable scroll 7 is hardened by nickel plating, and no sliding contact between the hydraulic projection 9B and the scroll substrate 7a is welded. Moreover, it does not weld in the sliding contact site | part of the hydraulic pressure plate 13 of steel and 9A of aluminum hydraulic protrusion parts.

In the state of FIG. 2 and FIG. 3, the movable scrolls 7 are in a 180 ° revolving position relationship with each other. In Fig. 2, the revolving position of the movable scroll 7 is in the highest position, and the element for preventing rotation 10 is about the peripheral surface of the revolving position regulating hole 7c on the scroll substrate 7a side. It touches the lowest part. The revolving ring 9 rotates about the rotational axis L1 of the rotating shaft 3 (the movable scroll 7) by contact with the lowest part of the peripheral surface of the revolving position regulating hole 7c of the element for preventing rotation 10. It is biased toward the idle position of the movable scroll 7 from the center) side. Therefore, the element 10 for autorotation is in contact with the uppermost part with respect to the circumferential surface of the idle position regulating hole 13b on the hydraulic plate 13 side.

When the eccentric shaft 4 idles 180 degrees in the state of FIG. 2, the idle position of the movable scroll 7 moves to the lowest moving position. As a result, the magnetic element 10 is in contact with the uppermost part of the peripheral surface of the idle position regulating hole 7c. The pivot ring 9 is moved from the movable scroll 7 on the rotation axis line L1 side of the rotation shaft 3 by contact with the uppermost part of the peripheral surface of the idle position regulating hole 7c of the element 10 for preventing rotation. It is biased toward the idle position. Therefore, the element 10 for preventing rotation is in contact with the lowest part of the circumferential surface of the idle position regulating hole 13b.

That is, according to the revolution of the movable scroll 7, the element 10 for preventing rotation slides in contact with the circumferential surface of the idle position regulating holes 2b and 7c, and the turning ring 9 slides around the idle center. It is biased by the idle position axis | shaft of the movable scroll 7 at the side. Therefore, the circumferential surface portion of the idle position regulating hole 2b in contact with the rotation blocking element 10 is 180 ° opposite to the contact portion between the rotational blocking element 10 and the circumferential surface of the idle position regulating hole 7c. To the position of.

In the case where the diameter D of the idle position regulating holes 13b and 7c and the diameter of the rotation preventing element 10 are set to d, when the state shifts from the second degree state to the third degree state, the rotating element 10 The idle position control is moved relative to each of (13b, 7c) by (Dd).

This value is equal to the idle radius r of the bush 6. Therefore, a relationship of D = d + r is set between the diameter D of the idle position regulating holes 13b and 7c, the diameter d of the element 10 for preventing rotation, and the idle radius r of the bush 6. By this relationship, the idle radius of the movable scroll 7 is defined as r.

Although the circumferential surface of the rotation preventing element 10 and the idle position regulating hole 13b are in sliding contact, the sliding contact portions are not welded because they are different members. In addition, although the peripheral surface of the rotation preventing element 10 and the idle position regulating hole 7c is in sliding contact, since the peripheral surface of the idle position regulating hole 7c is hardened by nickel plating, a sliding contact part is made into a sliding contact part. There is no welding.

The turning ring 9 attempts to rotate around the rotational axis L ₂ of the bush 6. However, the rotation preventing element 10 in contact with the idle position regulating hole 13b on the side of the hydraulic plate 13a prevents the revolution ring 9 from revolving in the circumferential direction by the statically placed idle position regulating hole 13b. Stop it. This idle stop occurs for all idle positions of the turning ring 9. Therefore, the turning ring 9 does not rotate around the central axis L2 of the bush 6.

The movable scroll 7 attempts to rotate around the rotational axis L2 of the bush 6. However, the revolving position regulating hole 7c on the axis of the scroll substrate 7a prevents revolving of the revolving ring 9 in the circumferential direction by the element 10 for preventing rotation on the revolving revolving ring 9. This idle stop occurs for all idle positions of the movable scroll 7. That is, the movable scroll 7 does not rotate around the center axis line L ₂ of the bush 6.

In the scroll type compressor of the present embodiment in which the movable scroll is idle without rotating, the turning ring is reduced by one compared with the conventional apparatus of Japanese Patent Laid-Open No. 59-28082. High precision is required for the machining of the peripheral ends of the idle position regulating holes 13b and 7c.

In the conventional apparatus of Japanese Patent Application Laid-Open No. 59-28082, which accepts both the compression reaction force transmission and the anti-rotation function in the cylindrical bearing element, the accuracy of machining the peripheral edges of all pockets must be increased. In the present embodiment in which the hydraulic protrusions 9A and 9B accept the compression reaction force transmission, there are four elements 10 for preventing rotation. However, the number of elements 10 for preventing rotation is sufficient, and the idle position regulation is sufficient. The number of the holes 13b and 7c is also sufficient at least three each.

Therefore, it is possible to shorten the machining time of the idle position regulating hole requiring high machining accuracy and to reduce the cost.

In addition, in the present embodiment in which the hydraulic plate 13 is interposed between the hydraulic wall 2a and the slewing ring 9, the front housing 2 can be made of aluminium, which is light in wear resistance. Therefore, the whole compressor can be reduced in weight.

The hydraulic pressure plate 13 which results in a reduction in the weight of the compressor receives the sliding contact action of the rotating element 10 for pivoting, and attempts to turn following the rotation of the rotating element 10. However, this following turning is prevented by the fitting action of the fitting protrusion 13a and the fitting recess 2b.

The fixing method by fitting the fitting projection 13a formed integrally with the hydraulic plate 13 and the fitting recess 2b on the front housing 2 side reduces the number of parts as compared with the fixing method by pin pressing. . In order to avoid the pin from being pulled out, it is necessary to set an exact size relationship between the pin diameter and the press hole diameter. Even if an exact size relationship is set between the pin diameter and the press-in hole diameter, the press-in operation of the pin itself is difficult. Since the hydraulic plate 13 of this embodiment is pressed against the hydraulic wall 2a by the compression reaction force, the hydraulic plate 13 does not space apart from the hydraulic wall 2a. Therefore, what is necessary is just to set the fitting precision of the fitting projection part 13a and the fitting recessed part 2b so that the hydraulic plate 13 may not rotate, and high processing precision like a pin press method is not required. In addition, the joining operation of the hydraulic plate 13 to the hydraulic wall 2a is much easier than the pin pressing operation.

The present invention is of course not limited to the above embodiment, for example, by installing the swing ring 9a as shown in FIG. 5 and transmitting the compression reaction force from the scroll substrate 7a to the hydraulic plate 13. An embodiment in which the hydraulic element 14 for insertion is inserted into the insertion through hole 9a is also possible.

Moreover, even if a hydraulic plate is bonded to the scroll substrate of a movable scroll, in this case, a fitting protrusion may be provided in the outer peripheral end side of a hydraulic plate, and a fitting recess may cut out and form the outer peripheral end of a scroll substrate.

As described above, the present invention interposes the swing ring between the scroll substrate of the movable scroll and the hydraulic wall, and interposes the swing ring between the hydraulic wall or the scroll substrate and the swing ring, and sandwiches the hydraulic plate side. The fitting projection is fitted to the fitting recess on the side to be bonded, and the hydraulic plate is bonded to the hydraulic wall or the scroll substrate, thereby reducing the number of rotation preventing elements that are responsible for the anti-rotation function and requiring high processing accuracy. It is possible to reduce the number of position regulating holes, and to achieve an excellent effect of reducing the number of parts, thereby improving the assembly work.

Claims (1)

A scroll compressor for forming a compression chamber that decreases in volume according to the revolution of the movable scroll between the fixed scroll and the movable scroll which is non-rotatingly supported against the fixed scroll, wherein the compression chamber acts on the movable scroll. The swing ring is placed between the hydraulic wall receiving the compression reaction force and the scroll board of the movable scroll, and a plurality of elements for rotating stops are fixedly attached to both surfaces of the swing ring, respectively. A hydraulic plate is provided at least on one side between the ring and between the scroll substrate and the pivot ring. A fitting protrusion is provided on the hydraulic plate, and a fitting recess is provided on the joining side of the hydraulic plate. The fitting projections are fitted to the fitting recesses to be fitted to at least one of the hydraulic wall and the scroll substrate. Plates are bonded to each other, and a plurality of idle position regulating holes are arranged in the circumferential direction on the scroll substrate side and the hydraulic side wall, respectively. A hydraulic element for transmitting a compression reaction force in the compression chamber acting on the movable scroll through a rotation blocking element on the other side of the swing ring in the idle position regulating hole on the scroll substrate side between the scroll substrate and the hydraulic wall. A scroll compressor characterized by intervening.