KR970009960B1 - Scroll compressor - Google Patents

Abstract

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Description

Scroll compressor

1 is an essential part cross sectional view of the compressor of the first embodiment;

2 is a cross-sectional view taken along the line B-B of FIG. 1 with respect to the main part of the compressor of the first embodiment.

3 is a sectional view of principal parts of a compressor of a second embodiment.

4 is a sectional view taken along the arrow C-C line in FIG. 3 with respect to the main part of the compressor of the second embodiment.

5 is a longitudinal sectional view of a compressor of the prior art.

6 is a cross-sectional view of an essential part of the conventional compressor.

Explanation of symbols on the main parts of the drawings

33: drive shaft 33a: inner diameter of the large diameter portion

62: driving bush 63: counter weight

63b: counterbore (concave) 62b, 63c, 62c, 63d: concave and convex

61: slide key S: sliding direction

Industrial use field

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to an improvement of a counterweight and a drive bush.

Conventional technology

As a conventional scroll compressor (hereinafter, simply referred to as a compressor), for example, one disclosed in Japanese Patent Application Laid-Open No. 57-83291 is known. In the compressor, a fixed scroll consisting of a fixed side plate and a fixed vortex is fixed in the housing, and a movable scroll made of a movable side plate and a movable vortex is engaged with each other by 180 degrees out of phase. In addition, the drive shaft is rotatably supported through the bearing in the housing, and an eccentric pin is formed in the inner end of the large diameter portion of the drive shaft. The eccentric pin is fitted with a drive bush which supports only the movable scroll through the bearing by acting in cooperation with the anti-rotation mechanism, and a counterweight is similarly fitted between the inner end of the large diameter portion and the drive bush. .

In this type of compressor, the rotation of the drive shaft is an orbital movement of the movable scroll by the driving bush and the anti-rotation mechanism, whereby the compression chamber formed by the engagement of the fixed scroll and the movable scroll sequentially reduces the volume while sequentially reducing the volume. The refrigerant is sucked into the compression chamber from the fluid inlet, and the refrigerant in the compression chamber is sequentially compressed and discharged into the discharge chamber. At this time, the counterweight offsets the eccentric moment that the drive bushing receives from the movable scroll to absorb the dynamic imbalance of the movable scroll.

Specifically, the following compressors are known.

As shown in Figs. 5 and 6, the compressor has a fixed side plate 21, a shell portion 22 forming an outline formed integrally with the fixed side plate 21, and fixed. The fixed scroll 2 which consists of the fixed spiral winding 23 formed in the involute curve etc. inside the side plate 21 has the movable side plate 41 and the involute curve inside this movable side plate 41. The compression chamber 39 is formed by engaging with the movable scroll 4 comprised of the movable spiral winding 42 formed by the back.

In the prote housing 30 coupled by the shell 22 and the fastening means of the fixed scroll 2, via the shaft sealing device 31 and the main bearing 32, as shown in FIG. Reference numeral 33 denotes a circular columnar eccentric plate 34 having an 0-axis axis as an eccentricity and protruding from each other. The drive bush 36 in which the eccentric hole 36a into which this eccentric pin 34 is inserted is protruded is also formed in a circular column shape centering on the Q line, and is connected to the eccentric pin 34 by a circlip (51). Combined through). The drive bush 36 supports the movable scroll 4 via the bearing 38 so that only the distance R is eccentric and only revolving by the cooperation with the anti-rotation mechanism 36.

In the drive bush 36, a pin (screw possible: 36b) is planted and installed in the large-diameter side of the drive shaft 33, and the count weight 35 is provided to the drive bush 36 by this pin 36b. The relative rotation is impossible. Moreover, the pin 36b protrudes to the drive shaft side, and is inserted in the recessed part 33b provided in the inner end part of the drive shaft 33. As shown in FIG. The count weight 35 is provided with an eccentric hole 35a through which the eccentric pin 34 is inserted.

In addition, as shown in FIG. 5, the front housing 30 is provided with a refrigerant inlet 8 facing the circumferential surface of the count weight 35 and passing through the refrigeration circuit. By passing through the front housing 30 and a part of the anti-rotation mechanism 37 through this refrigerant intake port 8, the suction path 9 communicates with the counting weight 35 and communicates directly with the compression chamber 39. have. Moreover, the discharge port 11 which communicates with the compression chamber 39 of a discharge step is penetrated by the center part of the fixed side plate 21 of the fixed scroll 2. As shown in FIG. The rear housing 10 is fixed to the fixed scroll 2, and the discharge port 11 communicates with the discharge chamber 13 formed inside the rear housing 10 via the check valve 12, and discharge chamber 13 ) Communicates with the refrigeration circuit as a refrigerant discharge port (not shown).

In this compressor, the drive shaft 33 is rotated via an electromagnetic clutch or the like. As a result, the eccentric pin 34 shown in FIG. 6 is driven to rotate about the shaft center 0, and the drive bush 36 drives the movable scroll 4 in cooperation with the rotation preventing mechanism 37. It revolves by the amount of eccentricity (R) centering on (0). Then, the compression chamber 39 formed by the fixed side plate 21, the fixed swirling body 23, the movable side plate 41, and the movable swirling body 42 shown in FIG. 5 sequentially builds a volume while centering the volume. The refrigerant is sucked into the compression chamber 39 from the refrigerant inlet 8 via the suction passage 9 by the refrigeration circuit so as to move to the. Thereafter, the refrigerant compressed by the movement of the compression chamber 39 presses the check valve 12 to open and is sucked into the discharge chamber 13 from the discharge port 11. At this time, the count weight 35 cancels the eccentric moment which the drive bush 36 received from the movable scroll 4, and absorbs the dynamic imbalance of the movable scroll 4.

Problems to be Solved by the Invention

However, in the above conventional compressor, the count weight is riveted to the drive bush, and the protruding portion of the rivet toward the drive shaft side is inserted into the concave recess provided in the drive shaft so as to be able to flow. Therefore, the driving bush is allowed to adjust the rotational movement around the eccentric pin defined in the flow range of the projecting portion, thereby absorbing the slight difference caused in the oblique positional relationship of the two vortices.

However, when the compressor is stopped, due to the relative induction of the recess and the protrusion due to the transmission torque between the drive bush and the counterweight and the drive shaft, an excessive shear force accompanied by a collision is applied to the rivet. Repetition is not just a deformation of the rivets, but sometimes a breakthrough. However, there is a problem that the manufacturing and assembly processes are complicated when the drive shaft and the counter weight are manufactured integrally or the counter weight and the drive bush are integrally manufactured.

An object of the present invention is to securely support a torque transmitted between a drive bush and a counterweight and a drive shaft at the time of starting and stopping in a compressor having a counter waiter as a separate component from the drive shaft and the drive bush. .

Means to solve the problem

(1) In order to solve the above problems, in the compressor of the present invention, a fixed scroll, a movable scroll which forms a compression chamber by engaging with the fixed scroll, and rotationally supported by a bearing are provided so that the slide key is located inside the large diameter section. Is fitted to the slide key so as to slide in a linear direction inclined opposite to the rotational direction of the drive shaft, and protrudes from the rotating shaft to allow the revolution of the movable scroll through the bearing in cooperation with the anti-rotation mechanism. And a counterweight disposed around the slide key to absorb the dynamic imbalance of the movable scroll, wherein the compression chamber sucks the refrigerant gas by the idle movement of the movable scroll and A scroll compressor for raising and discharging pressure, wherein the driving bush and the counterway In addition, the counterweight is impossible to engage in relative rotation, and new countermeasures are devised in which the counter weight is formed with a circular recess in which the counterweight is slidably fitted to allow the inner end of the large diameter portion of the drive shaft and the adjustment linear slide.

(2) In the compressor of the present invention, the counterweight is provided by fitting the slide key between the inner end of the large diameter portion of the drive shaft and the drive bush, and the coupling of the drive bush and the counterweight is in the sliding direction of the drive bush. It can achieve by fitting the recessed part and convex part extended in the direction which cross | intersects.

Action

In the compressors of claims 1 and 2, the drive bush and the counterweight are coupled so that relative rotation is impossible, and the recess formed in the counterweight is fitted so that the inner end of the large diameter portion of the drive shaft is movable.

In the compressors of claims 1 and 2, the drive bush and the counterweight are coupled to each other so that relative rotation is impossible, and the inner end of the large diameter portion of the drive shaft is inserted into the recess formed in the counterweight so as to be movable.

Further, in the compressors of claims 1 and 2, a limited straight line slide by a slide key is allowed with respect to the counterweight and the driving bush by the gap between the recesses that can be inserted therein, whereby the counterweight is driven. Together with the bush, it absorbs the slight differences resulting from the relative positional relationship between the two vortices.

At the time of starting and stopping the compressor of claims 1 and 2, the relative flow between the recessed portion and the inner diameter of the large diameter portion of the drive shaft due to the transfer torque between the drive shaft and the drive shaft of the counterweight is generated. The accompanying force is suitably supported by the arcuate contact of both.

In the compressor according to claim 2, the counterweight and the driving bush do not need to be penetrated through the rivet holes, respectively, nor do they need to secure the rivets conventionally employed as parts. Here, the fitting between the driving bush and the counterweight is eccentrically formed with respect to the eccentric pin, or the fitting between the recess and the convex portions of the driving bush and the counterweight intersects with the sliding direction of the driving bush. By extending, no substantial relative flow occurs, and no support is caused to offset the eccentric moment that the counterweight receives from the movable scroll via the driving bush.

Further, in the compressors of claims 1 and 2, since the counterweight is a separate component from the drive shaft and the drive bush, the counterweight can be easily manufactured and assembled as compared with the case of manufacturing and assembling a complex drive shaft and drive bush. have.

Example

Example 1

EMBODIMENT OF THE INVENTION The 1st Example which actualized the invention of Claims 1 and 2 is demonstrated referring drawings.

In this compressor, as shown in FIG. 1 and FIG. 2, a slide key 661 is formed at the inner end of the large diameter portion of the drive shaft 33 by providing two surface widths from the circumferential concave portion. The slide hole 62a through which the slide key 61 is inserted is provided therethrough. The counterweight 63 is provided with a slide hole 63a through which the slide key 61 is inserted. The slide key 61 is inserted into the slide holes 62a and 63a so that the circular lip 64 is supported by the projection end so that the driving bush 62 is adjusted to the slide key 61 in a straight line. It is slidably held together. The direction S in which the drive bush 62 slides by the slide key 61 is a linear direction inclined inversely to the rotation direction of the drive shaft 33.

Moreover, engagement of the drive bush 62 and the counterweight 63 is achieved by fitting the circular concave and convex parts 62b and 63c which cross | intersect the sliding direction S of the drive bush 62. FIG. The recessed part 62b and the convex part 63c are formed centering on the Q line which forms the external shape of the drive bush 62. As shown in FIG. Further, the counter weight 63 is formed with a circular counter bore 63b, which is inserted into the large diameter portion inner end 33a of the drive shaft 33 so as to be able to flow so as to allow adjustment straight slide.

In this compressor, the rotation of the drive shaft 33 is caused by the drive bush 62 and the anti-rotation mechanism through the slide key 61, which is a revolving motion of the movable scroll, and the refrigerant chamber is sucked, compressed and discharged by the compression chamber.

Here, in this compressor, the drive bush 62 can slide for a predetermined distance in the sliding direction S with respect to the slide key 61 by the driving force of the drive shaft 33, and the counter bore formed in the counter weight 63 Since the limited adjustment linear slide by the slide key 61 is permitted with respect to the counterweight 63 and the drive bush 62 by the flowable fit of 63b), the counterweight 63 is a drive bush ( And 62) absorb the slight differences in the relative positional relationship between the two vortices.

In this compressor, the driving bush 62 and the counterweight 63 are fitted with the circular recesses and the convex portions 62b and 63c to intersect the sliding direction S of the driving bush 62. This does not cause substantial relative flow and does not support the offset of the eccentric moment that the counterweight 63 receives from the movable scroll 4 via the driving bush 62.

Example 2

Embodiment 2 which embodies the invention of Claims 1 and 2 is demonstrated, referring drawings.

In this compressor, as shown in FIG. 3 and FIG. 4, the coupling of the drive bush 62 and the counterweight 63 is a recess and a convex part 62c orthogonal to the sliding direction S of the drive bush 62. FIG. , 63d). In addition, the parallel sliding surface of the slide key 61 is inscribed with a cross oil flaw 61a extending from the protruding end to the inner end 33a of the large diameter portion. Since the other structure is the same as that of Example 1, the same code | symbol is attached | subjected about the same structure and description is abbreviate | omitted.

In this compressor, since the concave portions and the convex portions 62c and 63c are formed in a straight line shape, the same operation as in the first embodiment can be exerted despite the easy manufacture.

In addition, in this compressor, since the oil groove 61a is engraved on the parallel sliding surface of the slide key 61, although it is extremely easy to manufacture, the drive bush 62 is driven by the oil groove 61a by the slide key ( Since 61 can slide suitably, the minute difference of both vortices can be suitably absorbed in the counterweight 63 and the drive bush 62. FIG.

Therefore, this compressor can exhibit more excellent durability while realizing manufacturing cost more cheaply.

Incidentally, in the first and second embodiments, the gap between the slide holes 63a and 62a and the slide key 61, and the gap between the inner end 33a of the large diameter portion of the drive shaft 33 and the counter bore 63b. By matching, the sliding ranges of the counterweight 63 and the driving bush 62 are regulated, but the clearance between the slide holes 63a and 62a and the slide key 61 and the inner diameter 33a of the large diameter portion of the driving shaft 33 The sliding range can be regulated by one side of the counter bore 63b.

As described above, in the compressors of claims 1 and 2, the driving bush and the counterweight are coupled to each other so as to be relatively rotatable, and the counterweight has a circular concave fitted to the inner end of the large diameter portion of the driving shaft so as to be able to flow. Since the part is formed, the torque transmitted between the drive bush and the counterweight and the drive shaft at the start and the stop is safely supported.

Accordingly, the compressors of claims 1 and 2 can exhibit excellent durability by not employing rivets or the like which may cause conventional variations.

Further, in the compressor according to claim 2, the machining process and the number of parts can be reduced from the reduction of rivets for fitting the drive bush and the counterweight.

Therefore, the compressor of claim 2 can reduce the manufacturing cost.

Further, in the compressors of claims 1 and 2, since the counterweight is a separate component from the drive shaft and the drive bush, the counterweight can be easily manufactured and assembled as compared with the case of manufacturing and assembling a complex drive shaft and drive bush. have.

Claims (2)

A sliding key (2), a movable scroll (4) which forms a compression chamber by engaging with the fixed scroll, and a slide key (61) on a large diameter portion inner end (33a) rotatably supported through a bearing (32). ) Is fitted to the slide key 61 so as to slide in a linear direction inclined opposite to the rotational direction of the drive shaft 33 and the drive shaft 33, and by the cooperation of the anti-rotation mechanism 37. A drive bush for eccentrically supporting the movable scroll 4 through a bearing so as to allow only revolution, and a counter weight disposed around the slide key 61 to absorb a dynamic imbalance of the movable scroll; In the scroll compressor in which the compression chamber 39 inhales the refrigerant gas and increases the pressure of the refrigerant gas by the idle motion of the driving chamber, the drive bush 62 and the counter weight 63 ) Is coupled to the relative rotation is impossible, and the counter weight is formed with a circular recess (63b) that is inserted into the large diameter inner end (33a) of the drive shaft (33) and flowable to allow a straight line to slide. Scroll type compressor characterized by. The counter weight (63) is installed between the large diameter inner end (33a) of the drive shaft (33) and the drive bush (62) by being fitted to the slide key (61). The engagement of the bush 62 with its counterweight 63 is achieved by fitting the recesses and the convex portions 62b, 62c, 63b, 63c extending in the direction crossing the sliding direction of the drive bush. Scroll type compressor characterized by.