JP3106739B2 - 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 compressor (hereinafter simply referred to as a compressor), a scroll compressor disclosed in Japanese Patent Application Laid-Open No. 2-176179 is known. In this compressor, a fixed scroll made up of a fixed side plate and a fixed scroll is fixed in a housing, and a movable scroll made up of a movable side plate and a movable scroll is meshed with the fixed scroll by 180 ° out of phase with each other. A drive shaft is rotatably supported on the housing via a bearing. A slide key is eccentrically protruded from the inner end of the large-diameter portion of the drive shaft, and a counter weight is integrally formed. . The slide key has a key axis inclined in a direction opposite to the rotation of the drive shaft, and a drive bush is slidably fitted to the slide key. The drive bush supports the orbiting scroll only through revolving through a bearing in cooperation with the rotation preventing mechanism.

In this compressor, the rotation of the drive shaft is caused to revolve by a drive bush and a rotation preventing mechanism via a slide key, whereby a compression chamber formed by the engagement of the fixed scroll and the movable scroll is formed. Since the refrigerant is moved toward the center while sequentially reducing the volume, 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.

[0004] At this time, the counterweight cancels the eccentric moment that the drive bush receives from the movable scroll, and absorbs the dynamic imbalance of the movable scroll. In addition, the drive bush is allowed to perform limited adjustment linear sliding along the key axis by fitting with the slide key. That is, the drive bush is adjusted by the driving force of the drive shaft in the direction of increasing the amount of eccentricity, and linearly slides to press the movable scroll of the movable scroll against the fixed scroll of the fixed scroll, thereby radially sealing the compression chamber. Is secured. At the same time, the drive bush can be adjusted and slid in the direction to reduce the amount of eccentricity, so that it absorbs the slight difference in the relative positional relationship between the two spiral bodies, and the movable scroll when the compressor is stopped or foreign matter is mixed. To avoid collision between the two spirals due to the reversal of.

[0005]

However, in the above-mentioned conventional compressor, since the counterweight is formed integrally with the inner end of the large-diameter portion of the drive shaft, there arises a problem that the manufacturing and assembling steps are complicated. On the other hand, when the counter weight is provided integrally with the drive bush, the manufacturing and assembly process is also complicated, and the adjustment linear sliding of the drive bush also causes
The counterweight also moves with the drive bush, and the sliding range of the drive bush is limited to a range where the counterweight having a large outer diameter does not interfere with the inner wall of the housing. In this case, even if the counterweight is finite in a minute range to offset the eccentric moment of the drive bush, a sufficient sealing force can be obtained because the range of the adjustment linear sliding in the direction of increasing the eccentricity is a problem. There is no. However, the range of adjustment linear sliding in the direction to reduce the amount of eccentricity involves the danger that both spiral bodies may be damaged in the event of an excessive load acting on the drive bush, It is not preferred to limit, but it is preferable to be as wide as possible.

SUMMARY OF THE INVENTION It is an object of the present invention to solve the above problem without complicating the manufacturing and assembling steps and preventing the two spiral bodies from being damaged even in an emergency.

[0007]

[Means for Solving the Problems]

(1) In the compressor of the first invention, in order to solve the above problem, a fixed scroll, a movable scroll that meshes with the fixed scroll to form a compression chamber, and a drive rotatably supported via a bearing. A shaft, a drive bush that supports the movable scroll only revolvably through a bearing in cooperation with a rotation prevention mechanism, and a counterweight that absorbs a dynamic imbalance of the movable scroll. A scroll compressor in which the compression chamber draws refrigerant gas by revolving motion and discharges the refrigerant gas while increasing the pressure of the refrigerant gas. The scroll compressor is eccentric to the inner end of the large-diameter portion of the drive shaft and inclined in the anti-rotation direction. A slide key having a key axis line is protruded, and the counter weight is protruded from the slide key so as to be fitted to the inner end of the large-diameter portion of the drive shaft so as to be relatively immovable. The ride key is provided with a novel means in which the drive bush is fitted so as not to rotate relative to the counter weight and to move relatively in the key axis direction.

(2) In the compressor according to the second aspect of the present invention, in order to solve the above problems, a fixed scroll, a movable scroll which meshes with the fixed scroll to form a compression chamber, and a rotatable bearing via a bearing. A drive bush that supports the orbiting scroll so that it can only revolve via a bearing in cooperation with the rotation preventing mechanism, and a counterweight that absorbs a dynamic imbalance of the orbiting scroll. A scroll type compressor in which the compression chamber sucks refrigerant gas by the orbital motion of a movable scroll and increases the pressure of the refrigerant gas to discharge the refrigerant gas, wherein the counter weight moves relatively to the inner end of the large-diameter portion of the drive shaft. The counterweight is eccentrically fitted with a guide portion having an eccentric and anti-rotationally inclined guide axis. A novel measure is taken in that the drive bush is fitted so as not to rotate relative to the gate and to be relatively movable in the guide axis direction.

[0009]

According to the compressors of the first and second aspects of the invention, the counterweight of a component independent of the drive shaft and the drive bush is fitted to the inner end of the large-diameter portion of the drive shaft. Since the counterweight is an independent component as described above, manufacture and assembly are easier than in the case of manufacturing a drive shaft and a drive bush having a complicated shape.

The counterweight does not move relative to the drive shaft. Here, in the compressor of the first invention, the drive bush is fitted to the slide key such that the drive bush cannot rotate relative to the counterweight and can move relatively in the key axis direction. In the compressor according to the second aspect of the present invention, the drive bush is fitted to the guide portion so as not to be rotatable relative to the counterweight and to be relatively movable in the guide axis direction of the counterweight. For this reason, in the compressors of the first and second inventions, even when the drive bush is adjusted to slide linearly, the counter weight having a large outer diameter does not move accompanying the drive bush, and the inner weight of the housing is taken into consideration. The sliding range of the drive bush is not limited. Therefore, since the drive bush can be slid linearly enough to adjust the eccentricity in a direction to reduce the eccentricity, even in the event of an excessive load acting on the drive bush, there is a slight positional relationship between the two spiral bodies. The difference is appropriately absorbed, and collision between the two scrolls due to the reverse rotation of the movable scroll when the compressor is stopped or when foreign matter is mixed is reliably avoided.

[0011]

【Example】

(Embodiment 1) Hereinafter, Embodiment 1 of the first invention will be described 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 spiral formed inside the fixed side plate 21 by an involute curve or the like. The fixed scroll 2 including the body 23 includes a movable side plate 41,
A movable scroll 4 including a movable scroll 42 formed by an involute curve or the like inside the movable side plate 41.
The compression chamber 39 is formed by meshing.

As shown in FIG. 2, a front housing 30 connected to the shell portion 22 of the fixed scroll 2 by fastening means is provided with a shaft sealing device 31 and a main bearing 32 therebetween.
A drive shaft 33 is rotatably supported about the O line as an axis, and a slide key 3 is provided on the inner end 33a of the large diameter portion of the drive shaft 33.
4 are formed. The slide key 34 passes through a point P from a cylindrical projection centered on the center line P,
Is formed by providing a two-plane width in parallel with the key axis S inclined in the anti-rotation direction.

A through hole 35a is formed in the counterweight 35, and a counterbore 35b of a center line O is formed on the large-diameter portion inner end 33a side.
4 is press-fitted, and the large-diameter portion inner end 33a is press-fitted into the counterbore 35b. I have.

As shown in FIG. 3, the drive bush 36 extends along the key axis S and is provided finitely in the direction of increasing the amount of eccentricity R and infinitely in the direction of decreasing the amount of eccentricity R. A slide hole 36a is formed through the slide hole 36a.
The slide key 34 is inserted so as to be slidable in a linear manner.
The circlip 51 is locked at a protruding end of the slide key 34 inserted into the slide hole 36a. The drive bush 36 is formed in a columnar shape with the Q line as a center line, and supports the movable scroll 4 via a bearing 38 so as to be able to revolve only through cooperation with a rotation preventing mechanism 37.

As shown in FIG. 1, the front housing 30 is provided with a refrigerant suction port 8 communicating with the refrigeration circuit, facing the peripheral surface of the counter weight 34. 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 shown in FIG. 1 is rotated via an electromagnetic clutch or the like. As a result, FIG.
Is driven around the axis O, and the drive bush 36 revolves the movable scroll 4 by the amount of eccentricity R about the axis O in cooperation with the rotation preventing mechanism 37. The compression chamber 39 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. 1 is moved toward the center while sequentially reducing the volume. The refrigerant is sucked into the compression chamber 39 from the refrigerant suction port 8 through the suction passage 9. 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,
The dynamic imbalance of the movable scroll 4 is absorbed.

Here, in this compressor, the counter weight 35 does not move relative to the drive shaft 33, and the drive bush 36 does not move.
Is provided on the slide key 34 so as to be slidable in parallel with the key axis S, so that only the drive bush 36 can be slid linearly as shown in FIGS. In this case, since the counter weight 35 having a large outer diameter does not move accompanying the driving bush 36, the sliding range of the driving bush 36 is not limited in consideration of the inner wall of the front housing 30.

At the time of such adjustment linear sliding, the drive bush 36
As shown in FIG. 4, as shown in FIG. 4, the eccentric amount R can be slid in a minute finite range by a driving force applied from the slide pin 34. Therefore, the drive bush 36 receives the eccentric moment of the orbiting scroll 4, and the eccentric moment is offset by the counterweight 35. In addition, the movable spiral 42 is also moved by the fixed spiral 2
2, and sufficient sealing force can still be obtained.

On the other hand, as shown in FIG. 5, the sliding range is infinite in the direction of decreasing the eccentric amount R,
The drive bush 36 can be adjusted linearly slidable until the slide key 34 comes into contact with the inner ring of the bearing 38 provided between the drive scroll 36 and the movable scroll 4. For this reason, the two spiral bodies 23, 4
2 and the reverse rotation of the orbiting scroll 4 when the compressor is stopped or foreign matter is mixed, even in the event that an excessive load acts on the drive bush 36, such a small difference is preferable. And the collision between the two spiral bodies 23 and 42 can be reliably avoided.

Further, 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 manufactured as compared with the case of manufacturing a driveshaft and drive bush having a complicated shape.・ Easy assembly. Therefore, this compressor can be manufactured at low cost without complicating the manufacturing and assembling processes, and exhibits excellent reliability without causing damage to the spiral bodies 23 and 42 even in the event of an emergency. can do. (Embodiment 2) Next, Embodiment 2 of the second invention will be described with reference to the drawings.

In this compressor, as shown in FIG. 6, a drive shaft 33 has a large-diameter portion inner end 33a having a square shaft 33b projecting therefrom, and a counterweight 35 having a shaft hole 35c formed therein.
The counterweight 35 has the square shaft 33b press-fitted into the shaft hole 35c, and the large-diameter portion inner end 3
By press-fitting 3a, it is fitted to the large-diameter portion inner end 33a of the drive shaft 33 so as to be relatively immovable.

As shown in FIG. 7, a guide projection 35d having a guide axis S eccentric to the drive bush 36 side and inclined in the anti-rotation direction is projected from the counter weight 35, as shown in FIG. A guided concave portion 36a that matches the guide convex portion 35d is provided on the counter weight 35 side. The guided concave portion 36a extends in the guide axis S, and is provided finitely in the direction of increasing the eccentric amount R and infinitely in the direction of decreasing the eccentric amount R. This guided concave portion 36a
The guide projection 35d of the counter weight 35 is fitted so as to be slidable for adjustment linearly. The other configuration is the same as that of the first embodiment, and the detailed description of the same configuration will be omitted.

In this compressor, when the drive shaft 33 is rotated, the guide projection 35d shown in FIG. 6 is driven around the axis O, and the drive bush 36 is rotated.
The movable scroll 4 is revolved around the axis O by the amount of eccentricity R in cooperation with the above. Then, the refrigerant is sucked, compressed and discharged by the compression chamber 39. Here, in this compressor, the counter weight 35 does not move relative to the drive shaft 33, and the drive bush 36 is provided on the counter weight 35 so as to be slidable in parallel with the guide axis S. As shown in (1), only the drive bush 36 can be adjusted linearly slidable. For this reason, also in this compressor, the drive bush 36 is formed in consideration of the inner wall of the front housing 30.
Is not limited.

At the time of such adjustment linear sliding, the drive bush 36
8, can be slid in a small finite range in a direction to increase the amount of eccentricity R by a driving force applied from the guide convex portion 35d, as shown in FIG. Therefore, the eccentric moment is canceled by the counter weight 35, and a sufficient sealing force is obtained. On the other hand, as shown in FIG. 9, the sliding range is infinite in the direction of decreasing the eccentric amount R. At this time, in this compressor, the slide key 3 restricting the moving range of the drive bush 36 by the inner ring of the bearing 38 as in the first embodiment is used.
4, the guide bush 35d of the counterweight 35 that does not limit the moving range of the drive bush 36 is employed, so that the drive bush 36 slides more linearly than in the first embodiment. Can be. Therefore, even in an emergency situation in which an excessive load acts on the drive bush 36, the two spiral bodies 23 and 42 are not damaged.

Also in this compressor, since the counterweight 35 is a component independent of the drive shaft 33 and the drive bush 36, manufacture and assembly are easy. Therefore, this compressor can be manufactured at low cost without complicating the manufacturing and assembling processes, and exhibits excellent reliability without causing damage to both the spiral bodies 23 and 42 even in an emergency. be able to.

[0026]

As described in detail above, the compressor of the present invention employs the structure described in the claims, so that the manufacturing and assembling steps are not complicated and the Can be prevented from damaging both spiral bodies. Therefore, this compressor can be manufactured at low cost and can exhibit excellent reliability.

[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 cross-sectional view similar to FIG. 3, showing a state in which the drive bush is slid linearly in a direction to reduce the amount of eccentricity from the state of FIG.

5 is a cross-sectional view similar to FIG. 3, showing a state in which the drive bush is slid linearly in an increasing direction of the eccentricity from the state of FIG.

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

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

FIG. 8 is a cross-sectional view similar to FIG. 7, showing a state where the drive bush has slid linearly in a direction of decreasing the eccentricity from the state of FIG.

FIG. 9 is a cross-sectional view similar to FIG. 7, showing a state in which the drive bush is slid linearly in an increasing direction of eccentricity from the state of FIG.

[Explanation of symbols]

2 ... fixed scroll 4 ... movable scroll 39 ...
Compression chamber 32 ... Main bearing 33 ... Drive shaft 37 ...
Anti-rotation mechanism 38 ... Bearing 36 ... Drive bush 35 ...
Counter weight 33a: Large-diameter portion inner end 34: Slide key S: Key axis, guide axis 35d: Guide convex part (guide part)

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Tetsuya Yamaguchi 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (56) References JP-A-2-176179 (JP, A) 4-49685 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F04C 18/02 311

Claims (2)

(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, a drive bush for supporting the movable scroll so that it can only revolve via the bearing in cooperation with a rotation preventing mechanism, and a dynamic imbalance of the movable scroll is absorbed. Including a counter weight to
A scroll compressor in which the compression chamber draws in refrigerant gas by the orbital motion of the orbiting scroll and increases the pressure of the refrigerant gas to discharge the refrigerant gas. A slide key having a key axis inclined in the rotation direction is protrudingly provided, and the counter weight is protruded from the slide key and fitted to the inner end of the large-diameter portion of the drive shaft so as to be relatively immovable. A scroll-type compressor, wherein the drive bush is fitted so as not to rotate relative to a counterweight and to move relatively in the key axis direction. 2. A fixed scroll, a movable scroll that meshes with the fixed scroll to form a compression chamber,
A drive shaft rotatably supported via a bearing, a drive bush for supporting the movable scroll so that it can only revolve via the bearing in cooperation with a rotation preventing mechanism, and a dynamic imbalance of the movable scroll is absorbed. Including a counter weight to
A scroll compressor in which the compression chamber sucks refrigerant gas by the orbital motion of the orbiting scroll and discharges the refrigerant gas while increasing the pressure of the refrigerant gas. The counterweight is immovably fitted, and the counterweight is formed with a guide portion having a guide axis that is eccentric and inclined in the anti-rotation direction. A scroll compressor in which the drive bush is fitted so as to be relatively movable in an axial direction.