JP3111707B2 - Scroll compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art As a conventional scroll type compressor (hereinafter simply referred to as a compressor), for example, Japanese Utility Model Laid-Open No. 57-8329.
No. 1 is known. In this compressor,
A fixed scroll made up of a fixed side plate and a fixed scroll is fixed in the housing, and a movable scroll made up of a movable side plate and a movable scroll is attached to the fixed scroll.
° The teeth are shifted in phase. A drive shaft is rotatably supported on the housing via a bearing, and an eccentric pin is implanted at the inner end of the large-diameter portion of the drive shaft.
The eccentric pin is fitted with a drive bush that supports the orbiting scroll so that it can only revolve via a bearing in cooperation with the rotation prevention mechanism. Similarly, a counterweight is provided between the inner end of the large diameter portion and the drive bush. Are fitted.

[0003] In this type of compressor, the rotation of the drive shaft is revolved by the drive bush and the rotation preventing mechanism to revolve the movable scroll, whereby the compression chamber formed by the engagement of the fixed scroll and the movable scroll sequentially increases the volume. Since the refrigerant is moved toward the center while being reduced, the refrigerant is sucked into the compression chamber from the fluid suction port, and the refrigerant in the compression chamber is sequentially compressed and discharged to the discharge chamber. At this time, the counter weight is
The drive bush cancels out the eccentric moment received from the movable scroll and absorbs the dynamic imbalance of the movable scroll.

[0004]

However, in the above-mentioned conventional compressor, the counterweight is rivet-coupled to the drive bush, and a protruding portion of the rivet protruding toward the drive shaft is provided with a bottomed hole formed in the drive shaft. Is loosely fitted. Therefore, the drive bush is allowed to adjust and rotate around the eccentric pin limited to the play range of the projecting portion, thereby absorbing a slight difference in the relative positional relationship between the two spiral bodies. However,
When starting and stopping the compressor, excessive shear force accompanying collision with the rivet acts due to relative movement between the bottomed hole and the protruding portion due to the transmission torque between the drive bush and the counterweight and the drive shaft. However, this repetition is not limited to deformation of the rivet, and may sometimes progress to breakage. On the other hand, if the drive shaft and the counterweight are manufactured integrally, or if the counterweight and the drive bush are manufactured integrally, there arises a problem that the manufacturing and assembling process becomes complicated.

The present invention relates to a compressor in which a counterweight is a component independent of a drive shaft and a drive bush. In a compressor, the torque transmitted between the drive bush and the counterweight and the drive shaft at the time of starting and stopping is secured. Is an issue to be solved.

[0006]

[Means for Solving the Problems]

(1) In order to solve the above-mentioned problems, the compressor according to the first invention is rotatably supported via a fixed scroll, a movable scroll which meshes with the fixed scroll to form a compression chamber, and a bearing. A drive shaft having an eccentric pin protruding from the inner end of the radial portion; a drive bush fitted to the eccentric pin and supporting the movable scroll only revolvably via a bearing in cooperation with a rotation preventing mechanism; A counter weight disposed around the eccentric pin and absorbing a dynamic imbalance of the movable scroll, wherein the orbital motion of the movable scroll causes the compression chamber to suck refrigerant gas and increase the pressure of the refrigerant gas. In the discharging scroll type compressor, the drive bush and the counterweight are coupled to each other so as not to rotate relatively, and the counterweight has a large diameter portion of the drive shaft. Novel means of circular recesses loosely fitted to permit the end and the adjustment rotation are formed are taken.

(2) In the compressor of the first invention, the counterweight is provided between the inner end of the large-diameter portion of the drive shaft and the drive bush so as to be fitted to the eccentric pin. The connection with the weight can be achieved by fitting the circular uneven portion formed eccentrically to the eccentric pin. (3) In the compressor according to the second aspect of the present invention, in order to solve the above-mentioned problem, a fixed scroll, a movable scroll which meshes with the fixed scroll to form a compression chamber, and are rotatably supported via bearings. A drive shaft with a slide key protruding from the inner end of the diameter portion, and fitted to the slide key so as to be slidable in a linear direction inclined in a direction opposite to the rotation direction of the drive shaft,
A drive bush for eccentrically supporting the orbiting scroll via a bearing in cooperation with a rotation preventing mechanism to support only the orbit, and a counterweight disposed around the slide key for absorbing a dynamic imbalance of the orbiting scroll In the scroll compressor in which the compression chamber sucks the refrigerant gas by the revolving motion of the orbiting scroll and increases and discharges the pressure of the refrigerant gas, the drive bush and the counter weight are relatively non-rotatable. While being connected, a novel measure is taken in which the counterweight is formed with a circular concave portion that is loosely fitted to the inner end of the large-diameter portion of the drive shaft so as to allow linear adjustment sliding.

(4) In the compressor according to the second aspect of the invention, the counter weight is provided between the inner end of the large-diameter portion of the drive shaft and the drive bush so as to be fitted to the slide key. The connection with the weight can be achieved by fitting a concave and convex portion extending in a direction intersecting the sliding direction of the drive bush.

[0009]

In the compressor according to the first to fourth aspects, the drive bush and the counterweight are connected to each other so as not to rotate relative to each other, and the inner end of the large-diameter portion of the drive shaft is loosely fitted into a recess formed in the counterweight. In the compressor according to the first and second aspects of the present invention, a limited adjustment rotation around the eccentric pin is allowed for the counterweight and the drive bush by the loose fitting gap of the concave portion. At the same time, it absorbs a slight difference in the relative positional relationship between the two spiral bodies.

Further, in the compressor according to the third and fourth aspects, due to the loose fitting gap of the concave portion, limited linear sliding of the counter weight and the drive bush by the slide key is allowed, whereby the counter weight is reduced. It absorbs a slight difference in the relative positional relationship between the two spiral bodies together with the drive bush. When the compressor according to any one of claims 1 to 4 is started and stopped, relative looseness occurs between the concave portion and the inner end of the large-diameter portion of the drive shaft due to the transmission torque between the drive bush and the counterweight and the drive shaft. The force accompanying the collision is preferably received by the contact between the two arc surfaces.

In the compressor according to the second and fourth aspects of the present invention, it is not necessary to previously form rivet holes in the counterweight and the drive bush, and it is not necessary to secure rivets and the like conventionally used as parts. . Here, the drive bush and the counterweight are formed such that the fitting of the two circular concave and convex portions is formed eccentrically with respect to the eccentric pin, or that the fitting of the two concave and convex portions intersects the sliding direction of the drive bush. Due to the extension, there is no substantial relative play, and the counterweight does not support the offset of the eccentric moment received from the movable scroll via the drive bush.

In the compressor according to the first to fourth aspects, since the counterweight is a component independent of the drive shaft and the drive bush, a case where the drive shaft and the drive bush having a complicated shape are manufactured and assembled is required. In comparison, it is easier to manufacture and assemble.

[0013]

【Example】

(Embodiment 1) A first embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the compressor includes a fixed side plate 21, a shell 22 formed integrally with the fixed side plate 21 to form an outer shell, and a fixed side plate 2.
The fixed scroll 2 including a fixed scroll 23 formed by an involute curve or the like inside the
A compression chamber 39 is formed by meshing with a movable scroll 4 comprising a movable scroll 42 formed by an involute curve and the like inside the movable side plate 41.

As shown in FIG. 2, through a shaft sealing device 31 and a main bearing 32, a front housing 30 is connected to the shell portion 22 of the fixed scroll 2 by fastening means.
The drive shaft 33 is rotatably supported about the O line as an axis, and a cylindrical eccentric pin 34 having a P line as a center line is eccentrically protruded from the inner end of the large diameter portion of the drive shaft 33. The drive bush 36 in which the eccentric hole 36a into which the eccentric pin 34 is inserted is formed in a cylindrical shape having the Q line as a center line,
The eccentric pin 34 is fitted via a circlip 51. The driving bush 36 cooperates with the rotation preventing mechanism 37 to support the movable scroll 4 via a bearing 38 eccentrically by a distance R so that only the revolution is possible.

The drive bush 36 has a pin 36b (a screw may be used) implanted on the large diameter side of the drive shaft 33. The pin 36b couples the counter weight 35 to the drive bush 36 so as not to rotate relatively. ing. The pin 36b does not protrude toward the drive shaft 33. The counterweight 35 has an eccentric hole 35 into which the eccentric pin 34 is inserted.
a and the center line P of the eccentric pin 34
A counterbore 35b is formed as a circular concave portion having a center line (substantially O) different from that of FIG. This counterbore 35b has a substantially center line O different from the center line P of the eccentric pin 34, and its loose fitting gap is limited to the counterweight 35 and the drive bush 36 around the eccentric pin 34 (center line P). The adjustment rotation is set to be allowed. Thus,
The large-diameter portion inner end 33a of the drive shaft 33 is loosely fitted into the counterbore 35b.

As shown in FIG. 1, the front housing 30 is provided with a refrigerant suction port 8 which faces the peripheral surface of the counter weight 35 and communicates with the refrigeration circuit. The refrigerant suction port 8 communicates with a suction path 9 that penetrates through the front housing 30 and a part of the rotation preventing mechanism 37 to bypass the counterweight 35 and directly communicates with the compression chamber 39. Further, a discharge port 1 communicating with the compression chamber 39 at the discharge stage is provided at a central portion of the fixed side plate 21 of the fixed scroll 2.
1 is penetrated. A rear housing 10 is fixed to the fixed scroll 2, and a discharge port 11 is formed via a check valve 12 in a discharge chamber 1 formed inside the rear housing 10.
The discharge chamber 13 communicates with the refrigeration circuit at 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. 2 is driven to rotate about the axis O, and the drive bush 36 cooperates with the rotation preventing mechanism 37 to revolve the movable scroll 4 about the axis O by the amount of eccentricity R. . The compression chamber 3 formed by the fixed side plate 21, the fixed spiral body 23, the movable side plate 41, and the movable spiral body 42 shown in FIG.
Since the refrigerant 9 is moved toward the center while its volume is sequentially reduced, the refrigerant is drawn into the compression chamber 39 from the refrigerant suction port 8 through the suction passage 9 from the refrigerant circuit. Thereafter, the refrigerant compressed by the movement of the compression chamber 39 pushes and opens the check valve 12 and is discharged from the discharge port 11 to the discharge chamber 13. At this time, the counterweight 35 cancels the eccentric moment that the drive bush 36 receives from the movable scroll 4 and absorbs the dynamic imbalance of the movable scroll 4.

In this compressor, limited adjustment of the counterweight 35 and the drive bush 36 around the eccentric pin 34 (center line P) is performed by the loose fitting gap of the counterbore 35b formed on the counterweight 35. Since the rotation is allowed, the counter weight 35 is moved together with the drive bush 36 while the eccentric amount R is minutely changed.
It absorbs slight differences in the relative positional relationship between 3, 42.

When starting and stopping the compressor, FIGS.
As shown in FIG. 3, the counterbore 35 due to the transmission torque between the drive bush 36 and the counterweight 35 and the drive shaft 33 is provided.
Relative play occurs between b and the inner end 33a of the large-diameter portion of the drive shaft 33. In this case, the force accompanying the collision is favorably received by the large-area arc-shaped surface contact between them. Therefore, in this compressor, the torque transmitted between the drive bush 36 and the counterweight 35 and the drive shaft 33 at the time of starting and stopping can be safely received without using a conventional rivet or the like that may be deformed. As a result, excellent durability can be exhibited.

In this compressor, since the counterweight 35 is a component independent of the drive shaft 33 and the drive bush 36, the counterweight 35 is compared with a case where a drive shaft and a drive bush of a complicated shape are manufactured and assembled. Therefore, manufacture and assembly can be easily performed. (Embodiment 2) Next, a second embodiment of the present invention will be described with reference to the drawings.

In this compressor, as shown in FIG. 5, the connection between the drive bush 52 and the counterweight 53 is formed in a circular uneven portion 52b,
3c. Concave part 52b, convex part 5
3c is formed with the Q line forming the outer shape of the drive bush 52 as the center line. Also, as in the first embodiment, the large-diameter portion inner end 3 of the drive shaft 33 is provided on the back surface of the counterweight 53.
A circular counterbore 53b for loose fitting with 3a is formed. Other configurations are the same as those of the first embodiment, and thus the same configurations are denoted by the same reference numerals and description thereof will be omitted.

In this compressor, the counterweight 53 is non-rotatably connected to the drive bush 52 via the concave portion 52b and the convex portion 53c. 3
6b is not interposed. For this reason, it is not necessary to previously penetrate the rivet holes in the counter weight 53 and the drive bush 52, respectively, and the pins 36b
It is not necessary to secure such as parts. Here, the drive bush 52 and the counter weight 53 do not cause substantial relative play because the center line Q of the concave portion 52b and the convex portion 53c is different from the center line P of the eccentric pin 34.
The counterweight 53 does not support the offset of the eccentric moment received from the orbiting scroll 4 via the drive bush 52.

Therefore, in this compressor, the operation and effect of the first embodiment can be exhibited, and
6b and the like, the number of processing steps and the number of parts can be reduced, and the manufacturing cost can be reduced. (Embodiment 3) Next, a third embodiment of the present invention will be described with reference to the drawings.

In this compressor, as shown in FIGS. 6 and 7, a slide key 61 is formed at the inner end of the large-diameter portion of the drive shaft 33 by providing a two-sided width from a cylindrical projection. Is provided with a slide hole 62a through which the slide key 61 is inserted. The counter weight 63 has a slide hole 63 into which the slide key 61 is inserted.
a is penetrated. Slide key 61 is slide hole 6
The drive bush 62 is fixed to the slide key 61 such that the drive bush 62 can be adjusted and linearly slidable by being inserted into the 2a and 63a and the circlip 64 being locked to the projecting end. The direction S in which the drive bush 62 slides with the slide key 61 is a linear direction that is inclined opposite to the rotation direction of the drive shaft 33.

The connection between the drive bush 62 and the counterweight 63 is achieved by fitting of circular concave and convex portions 62b and 63c intersecting the sliding direction S of the drive bush 62. The concave portion 62b and the convex portion 63c are formed with the Q line forming the outer shape of the drive bush 62 as the center line, as in the second embodiment. On the back surface of the counterweight 63, as in the first and second embodiments, the large-diameter portion inner end 3 of the drive shaft 33 is provided.
A circular counterbore 63b which is loosely fitted to allow adjustment linear sliding with 3a is formed. Other configurations are the same as those of the second embodiment, and therefore, the same configurations are denoted by the same reference numerals and description thereof will be omitted.

In this compressor, the rotation of the drive shaft 33 is revolved by the drive bush 62 and the rotation preventing mechanism 37 via the slide key 61 to revolve the movable scroll 4. Inhalation, compression and discharge of Here, in this compressor, the driving bush 62 is slidable in the sliding direction S by a predetermined distance in the sliding direction S by the driving force of the driving shaft 33, so that the counterbore 63 b formed on the counter weight 63 can play. Because the fitting gap allows limited linear sliding of the counter weight 63 and the drive bush 62 with the slide key 61, the counter weight 63 is
At the same time, it absorbs a slight difference in the relative positional relationship between the two spiral bodies 23 and 42.

In this compressor, the drive bush 62
And the counter weight 63 are both circular concave and convex portions 62.
Since the engagement of the b and 63c extends in a direction intersecting the sliding direction S of the drive bush 62, no substantial relative movement occurs, and the counterweight 63 is moved by the movable scroll 4 via the drive bush 62. There is no support for offsetting the eccentric moment received from.

Therefore, also in this compressor, the same operation and effect as in the second embodiment can be exhibited. (Embodiment 4) A fourth embodiment of the present invention will be described with reference to the drawings.

In this compressor, as shown in FIGS. 8 and 9, the connection between the drive bush 62 and the counterweight 63 is made by the uneven portion 6 perpendicular to the sliding direction S of the drive bush 62.
This is achieved by fitting of 2c and 63d. The parallel sliding surface of the slide key 61 has a large diameter inner end 3
A cross-shaped oil groove 61a extending to 3a is formed. Other configurations are the same as those of the third embodiment, and therefore, the same configurations are denoted by the same reference numerals and description thereof will be omitted.

In this compressor, the concave and convex portions 62c, 6
Since 3d is formed in a straight line, the same operation as in the third embodiment can be exerted despite easy production. Further, in this compressor, the oil groove 61a is formed in the parallel sliding surface of the slide key 61, so that the drive bush 62 is formed by the oil groove 61a. Can be preferably slid, so that a small difference between the two spiral bodies 23 and 42 in the counter weight 63 and the drive bush 62 can be more suitably absorbed.

Therefore, in this compressor, more excellent durability can be exhibited while further reducing the production cost. In the third and fourth embodiments, the gap between the slide holes 63a and 62a and the slide key 61 and the gap between the large-diameter portion inner end 33a of the drive shaft 33 and the counterbore 63b are made to coincide with each other, so that The sliding range of the drive bush 62 is regulated, but the sliding range is regulated by one of a gap between the slide holes 63a, 62a and the slide key 61 and a gap between the large-diameter portion inner end 33a of the drive shaft 33 and the counterbore 63b. You can also.

[0032]

As described in detail above, in the compressor according to the first to fourth aspects, the drive bush and the counterweight are connected to each other so as not to rotate relative to each other, and the counterweight is connected to the inner end of the large-diameter portion of the drive shaft. Since the circular concave portion to be loosely fitted is formed, the torque transmitted between the drive bush and the counterweight and the drive shaft at the time of starting and stopping can be safely received.

Therefore, in the compressor of claims 1 to 4,
Since a conventional rivet or the like which may be deformed is not used, excellent durability can be exhibited. According to the compressors of the second and fourth aspects, the number of rivets or the like for fitting the drive bush and the counterweight is reduced, so that the number of processing steps and the number of parts can be reduced.

Therefore, in the compressor according to claims 2 and 4,
The manufacturing cost can be reduced. In addition, in the compressor of Claims 1-5, since a counterweight is a component independent of a drive shaft and a drive bush, compared with the case where a drive shaft and a drive bush of a complicated shape are manufactured and assembled. , Easily manufactured and assembled.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment.

FIG. 2 is a sectional view of a main part of the compressor according to the first embodiment.

FIG. 3 is a cross-sectional view taken along the line AA of FIG. 2, relating to a main part of the compressor of the first embodiment.

FIG. 4 is a sectional view similar to FIG. 3, showing a state where the drive shaft is rotated by a small angle from the state of FIG.

FIG. 5 is a sectional view of a main part of a compressor according to a second embodiment.

FIG. 6 is a sectional view of a main part of a compressor according to a third embodiment.

FIG. 7 is a cross-sectional view taken along line BB of FIG. 6, relating to a main part of the compressor of the third embodiment.

FIG. 8 is a sectional view of a main part of a compressor according to a fourth embodiment.

FIG. 9 is a cross-sectional view taken along the line CC of FIG. 8, relating to a main part of the compressor of the fourth embodiment.

[Explanation of symbols]

2 ... fixed scroll 4 ... movable scroll 39 ...
Compression chamber 32 Main bearing 34 Eccentric pin 33
Drive shaft 33a: Large-diameter portion inner end 37: Anti-rotation mechanism 36, 52, 62 ... Drive bush 35, 53, 63
... Counter weights 35b, 53b, 63b ... Counterbore (recess) 52b, 53c, 62b, 63c, 62c, 63d ... Uneven portion 61 ... Slide key S ... Sliding direction

──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Tetsuo Yoshida 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (72) Inventor Shinya Yamamoto 2-1-1, Toyota-cho, Kariya-shi, Aichi Co., Ltd. Inside Toyota Industries Corporation (72) Inventor Masao Iguchi 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (72) Inventor Kiyohiro Yamada 2-1-1, Toyota-machi, Kariya-shi, Aichi Prefecture Toyoda Automatic Corporation Inside the loom factory (72) Kunifumi Goto 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside the Toyota Industries Corporation (72) Inventor Tetsuya Yamaguchi 2-1-1, Toyota-machi, Kariya-shi, Aichi Prefecture Toyota Industries Corporation (58) Investigated field (Int.Cl. ⁷ , DB name) F04C 18/02 311

Claims (4)

(57) [Claims] 1. A fixed scroll, a movable scroll which meshes with the fixed scroll to form a compression chamber,
A drive shaft rotatably supported via a bearing and having an eccentric pin protruding at the inner end of the large-diameter portion, and fitted to the eccentric pin, cooperating with the rotation preventing mechanism to move the movable scroll through the bearing. A driving bush that is eccentric and supports only the revolution, and a counter weight that is disposed around the eccentric pin and absorbs a dynamic imbalance of the orbiting scroll; In a scroll type compressor for sucking gas and discharging while increasing the pressure of the refrigerant gas, the drive bush and the counterweight are coupled to each other so as not to rotate relatively, and the counterweight has a large diameter of the drive shaft. A scroll type compressor having a circular concave portion which is loosely fitted to allow the adjustment rotation to the inner end of the scroll type compressor. 2. The eccentric pin is provided between the inner end of the large-diameter portion of the drive shaft and the drive bush so as to be fitted to the eccentric pin. 2. The method according to claim 1, wherein the eccentric shape is achieved by fitting a circular concave and convex portion formed eccentrically with respect to the first direction.
The scroll-type compressor as described. 3. A fixed scroll, a movable scroll which meshes with the fixed scroll to form a compression chamber,
A drive shaft rotatably supported via a bearing and having a slide key protruding from the inner end of the large-diameter portion, and slidably fitted to the slide key in a linear direction inclined in a direction opposite to the rotation direction of the drive shaft. And a drive bush eccentrically supporting the orbiting scroll via a bearing in cooperation with the rotation preventing mechanism, and supporting only the revolving motion, and being arranged around the slide key to absorb a dynamic imbalance of the orbiting scroll. A scroll type compressor, wherein the compression chamber sucks refrigerant gas by the revolving motion of the orbiting scroll and increases the pressure of the refrigerant gas to discharge the refrigerant gas. The counterweight is formed so as to be non-rotatable, and has a circular concave portion that is loosely fitted to the inner end of the large-diameter portion of the drive shaft to allow adjustment linear sliding. A scroll compressor characterized by the following. 4. The driving mechanism according to claim 1, wherein the counterweight is provided between the inner end of the large-diameter portion of the drive shaft and the drive bush so as to be fitted to the slide key. 4. The scroll type compressor according to claim 3, wherein the compression is achieved by fitting of an uneven portion extending in a direction intersecting the sliding direction of the scroll.