JPH05302578A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To safely receive torque transmitted between a driving bush and a driving shaft and between a counterweight and the driving shaft at the time of starting and stopping, in a compressor in which the counterweight is formed as a constitutional part independent of the drive shaft and the driving bush. CONSTITUTION:A driving bush 36 and a counterweight 35 are connected so as not to relatively rotate, and a circular counterbore 35b fitted to float into a large contour part internal end 33a of a driving shaft 33 is formed in the counterweight 35. In this counterbore 35b, a play fit clearance is set in order to permit a limited adjusting turn about an eccentric pin 34 relating to the counterweight 35 and the driving bush 36, and a fine difference generated in a relative position relation between both volute units 23, 42 is absorbed by the counterweight 35 with the drive bush 36. At the time of starting and stopping a compressor, force according to collision by transmission torque is suitably received by contact of circular arc surface between the counterbore 35b and the large contour part internal end 33a.

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 improvements in counter weights and drive bushes.

[0002]

2. Description of the Related Art As a conventional scroll type compressor (hereinafter, simply referred to as a compressor), for example, JP-A-57-8329.
The one disclosed in Japanese Patent Publication No. 1 is known. With this compressor,
A fixed scroll composed of a fixed side plate and a fixed scroll is fixed in the housing, and a movable scroll composed of a movable side plate and a movable scroll is attached to the fixed scroll.
° It is meshed with a phase shift. A drive shaft is rotatably supported in the housing via bearings, and an eccentric pin is planted 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 movable scroll so that it can only revolve via a bearing in cooperation with a rotation prevention mechanism.A counter weight is similarly provided between the inner end of the large diameter portion and the drive bush. Are fitted.

In this type of compressor, the rotation of the drive shaft is revolved around the movable scroll by the drive bush and the rotation preventing mechanism, whereby the compression chambers formed by the meshing of the fixed scroll and the movable scroll sequentially increase in volume. Since the refrigerant is moved toward the center while being contracted, 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 into the discharge chamber. At this time, the counter weight is
It cancels the eccentric moment that the drive bush receives from the movable scroll, and absorbs the dynamic imbalance of the movable scroll.

[0004]

However, in the above-described conventional compressor, the counterweight is rivet-coupled to the drive bush, and the protruding portion of the rivet toward the drive shaft is formed in the drive shaft. Is loosely fitted to. Therefore, the drive bush is allowed to adjust and rotate around the eccentric pin, which is limited to the floating range of the protruding portion, so that a minute difference generated in the relative positional relationship between the two spiral bodies is absorbed. However,
When the compressor is started or stopped, an excessive shearing force with a collision is applied to the rivet due to the relative looseness between the bottomed hole and the protruding part due to the transmission torque between the drive bush and the counterweight and the drive shaft. However, this repetition is not limited to the deformation of the rivet, and there is a possibility that it may even progress to fracture. On the other hand, if the drive shaft and the counter weight are manufactured integrally, or if the counter weight and the drive bush are manufactured integrally, there arises a problem that the manufacturing / assembly process becomes complicated.

According to the present invention, in a compressor in which the counterweight is a component independent of the drive shaft and the drive bush, the torque transmitted between the drive bush and the counterweight and the drive shaft during starting and stopping is safe. It is an issue to be solved to accept it.

[0006]

[Means for Solving the Problems]

(1) In the compressor of the first invention, in order to solve the above-mentioned problems, a fixed scroll, a movable scroll that forms a compression chamber by meshing with the fixed scroll, and a rotatably supported bearing are provided. A drive shaft having an eccentric pin projecting from the inner end of the diameter portion; a drive bush fitted to the eccentric pin and supporting the movable scroll so that it can only revolve through a bearing in cooperation with a rotation preventing mechanism; A counterweight that is arranged around an eccentric pin and absorbs a dynamic imbalance of the movable scroll, and the compression chamber sucks the refrigerant gas and increases the pressure of the refrigerant gas by the revolution movement of the movable scroll. In a scroll type compressor for discharging, the drive bush and the counter weight are coupled to each other such that they cannot rotate relative to each other, and the counter weight 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 aspect of the present invention, the counter weight is provided by being fitted to the eccentric pin between the inner end of the large diameter portion of the drive shaft and the drive bush, and the drive bush and the counter are provided. The connection with the weight can be achieved by fitting the circular uneven portion formed eccentrically to the eccentric pin. (3) In the compressor of the second aspect of the invention, in order to solve the above-mentioned problems, a fixed scroll, a movable scroll that forms a compression chamber by meshing with the fixed scroll, and a rotatably supported bearing are used. A drive shaft having a slide key projectingly provided on the inner end of the diameter portion, and the slide key is slidably fitted in a linear direction inclined opposite to the rotation direction of the drive shaft,
A drive bush that eccentrically supports the movable scroll through a bearing in cooperation with a rotation preventing mechanism to support only the revolution, and a counter weight that is arranged around the slide key and absorbs the dynamic imbalance of the movable scroll. In a scroll type compressor that includes and, in which the compression chamber draws the refrigerant gas by the orbital motion of the movable scroll and increases the pressure of the refrigerant gas and discharges the refrigerant gas, the drive bush and the counterweight are relatively non-rotatable. A novel means has been taken in which, while being coupled, the counterweight is formed with a circular recess which is loosely fitted to the inner end of the large diameter portion of the drive shaft to allow adjustment linear sliding.

(4) In the compressor of the second invention, the counter weight 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 drive bush and the counter. The connection with the weight can be achieved by fitting an uneven 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 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 in the recess formed in the counterweight. In the compressor according to the first and second aspects of the invention, the loose fitting clearance of the recess allows a limited adjustment rotation around the eccentric pin with respect to the counter weight and the drive bush. At the same time, it absorbs a minute difference that occurs in the relative positional relationship between the two spiral bodies.

Further, in the compressor according to the third and fourth aspects, the loose fitting clearance of the recess allows the counterweight and the drive bush to perform limited adjustment linear sliding by the slide key. It absorbs a minute difference that occurs in the relative positional relationship between both spiral bodies together with the drive bush. When the compressor according to any one of claims 1 to 4 is started or stopped, relative movement between the concave portion and the inner end of the large diameter portion of the drive shaft occurs due to the transmission torque between the drive bush and the counter weight and the drive shaft. The force associated with the collision is preferably received by the contact of the two arc surfaces.

Further, in the compressors of claims 2 and 4, it is not necessary to previously pierce the counterweight and the drive bush with rivet holes, and it is not necessary to secure the rivet or the like that has been conventionally adopted as a component. .. Here, in the drive bush and the counterweight, the fitting of the circular concave and convex portions of both is formed eccentrically with respect to the eccentric pin, or the fitting of the concave and convex portions of both is in a direction intersecting the sliding direction of the drive bush. Due to the extension, there is no substantial relative movement, and there is no bearing for canceling the eccentric moment that the counterweight receives from the movable scroll via the drive bush.

In the compressor of claims 1 to 4, since the counterweight is a component independent of the drive shaft and the drive bush, it is different from the case where the drive shaft and the drive bush having a complicated shape are manufactured and assembled. By comparison, it is easily manufactured and assembled.

[0013]

【Example】

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

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

In the drive bush 36, a pin (a screw may be used) 36b is planted on the large diameter side of the drive shaft 33, and the counterweight 35 is connected to the drive bush 36 by the pin 36b so as not to rotate relative to the drive bush 36. ing. The pin 36b is not projected to the drive shaft 33 side. The counterweight 35 has an eccentric hole 35 into which the eccentric pin 34 is inserted.
a is pierced and the center line P of the eccentric pin 34 is
A counterbore 35b is formed as a circular concave portion having a center line (almost O) different from. The counterbore 35b has a substantially center line O different from the center line P of the eccentric pin 34, and the loose fitting gap is limited to the counter weight 35 and the drive bush 36 around the eccentric pin 34 (center line P). It is set so as to allow the adjusted rotation. Thus
The large diameter portion inner end 33a of the drive shaft 33 is loosely fitted in the spot facing 35b.

Further, as shown in FIG. 1, the front housing 30 is provided with a refrigerant suction port 8 facing the peripheral surface of the counterweight 35 and communicating with the refrigeration circuit. The refrigerant suction port 8 communicates with a suction passage 9 that directly penetrates the compression chamber 39 while avoiding the counterweight 35 by penetrating a part of the front housing 30 and the rotation preventing mechanism 37. Further, the discharge port 1 communicating with the compression chamber 39 at the discharge stage is provided in the central portion of the fixed side plate 21 of the fixed scroll 2.
1 is pierced. A rear housing 10 is fixed to the fixed scroll 2, and a discharge port 11 is formed inside the rear housing 10 via a check valve 12.
3, the discharge chamber 13 communicates with the refrigeration circuit through 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 rotationally driven about the axis O, and the drive bush 36 cooperates with the rotation preventing mechanism 37 to revolve the movable scroll 4 around the axis O with an eccentric amount 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 9 is moved toward the center while the volume is reduced successively, the refrigerant is sucked from the refrigeration circuit to the compression chamber 39 from the refrigerant suction port 8 through the suction passage 9. After that, the refrigerant compressed by the movement of the compression chamber 39 pushes the check valve 12 open and is discharged from the discharge port 11 to the discharge chamber 13. At this time, the counterweight 35 offsets the eccentric moment that the drive bush 36 receives from the movable scroll 4 and absorbs the dynamic imbalance of the movable scroll 4.

Here, in this compressor, due to the loose fitting gap of the counterbore 35b formed in the counterweight 35, the counterweight 35 and the drive bush 36 are limitedly adjusted around the eccentric pin 34 (center line P). Since the rotation is allowed, the counterweight 35, together with the drive bush 36, changes the eccentricity R slightly, and both counterbodies 2 are rotated.
It absorbs a slight difference generated in the relative positional relationship between No. 3 and 42.

3 and 4 when the compressor is started and stopped.
As shown in FIG. 5, the counterbore 35 by the transmission torque between the drive bush 36 and the counterweight 35 and the drive shaft 33.
Relative movement between b and the inner end 33a of the large-diameter portion of the drive shaft 33 occurs, but the force accompanying the collision at this time is favorably received by the large-area arc surface contact between the two. 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 adopting the conventional rivets or the like that may be deformed. Since it can be accepted, it can exhibit excellent durability.

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

In this compressor, as shown in FIG. 5, the driving bush 52 and the counter weight 53 are connected to the eccentric pin 34 so as to be eccentrically formed.
This is achieved by fitting 3c. Concave portion 52b, convex portion 5
3c is formed with the Q line forming the outer shape of the drive bush 52 as the center line. Further, on the back surface of the counterweight 53, as in the first embodiment, the large diameter inner end 3 of the drive shaft 33 is formed.
A circular counterbore 53b is formed so as to be loosely fitted to 3a. Since other configurations are the same as those of the first embodiment, the same components are designated by the same reference numerals and the description thereof will be omitted.

In this compressor, the counterweight 53 is connected to the drive bush 52 via the recess 52b and the projection 53c so as not to rotate relative to each other, and when the drive bush 52 and the counterweight 53 are connected, the pin as in the first embodiment is used. Three
6b is not interposed. For this reason, it is not necessary to previously pierce the counterweight 53 and the drive bush 52 with rivet holes, respectively, and the pin 36b that has been conventionally adopted is used.
It is not necessary to secure such as parts. Here, the drive bush 52 and the counterweight 53 do not cause substantial relative looseness because the center line Q of the recess 52b and the protrusion 53c is different from the center line P of the eccentric pin 34.
The counterweight 53 does not support the eccentric moment received from the movable scroll 4 via the drive bush 52.

Therefore, in this compressor, the action and effect of the first embodiment can be exhibited, and the pin 3
6b and the like can be reduced, so that the number of processing steps and the number of parts can be reduced, and the manufacturing cost can be reduced. (Embodiment 3) Next, an embodiment 3 embodying the invention of claims 3 and 4 will be described with reference to the drawings.

In this compressor, as shown in FIGS. 6 and 7, a slide key 61 is formed on the inner end of the large-diameter portion of the drive shaft 33 by providing a two-sided width from the cylindrical convex portion, and a drive bush 62 is formed. A slide hole 62a into which the slide key 61 is inserted is provided through. Further, the counterweight 63 has a slide hole 63 into which the slide key 61 is inserted.
a is pierced. Slide key 61 has slide hole 6
The drive bush 62 is fixedly slidable with respect to the slide key 61 by being inserted into 2a and 63a and locking the circlip 64 at the projecting end. The direction S in which the drive bush 62 slides by the slide key 61 is a linear direction that is inclined opposite to the rotation direction of the drive shaft 33.

The coupling between the drive bush 62 and the counterweight 63 is achieved by fitting the 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. Further, on the back surface of the counter weight 63, as in the first and second embodiments, the large diameter inner end 3 of the drive shaft 33 is formed.
A circular counterbore 63b is formed so as to loosely fit with 3a to allow adjustment linear sliding. Since other configurations are the same as those of the second embodiment, the same configurations are denoted by the same reference numerals and the description thereof will be omitted.

In this compressor, the rotation of the drive shaft 33 is revolved around the movable scroll 4 by the drive bush 62 and the rotation preventing mechanism 37 via the slide key 61, and the refrigerant is compressed by the compression chamber 39 as in the first embodiment. Inhale, compress, and discharge. In this compressor, the driving force of the driving shaft 33 allows the drive bush 62 to slide in the sliding direction S with respect to the slide key 61 by a predetermined distance, and the counterbore 63b formed in the counterweight 63 has a free play. Since the adjustment gap allows the counterweight 63 and the drive bush 62 to slide on the counterweight 63 and the drive bush 62 by a limited amount of adjustment straight line,
At the same time, it absorbs a slight difference in the relative positional relationship between the spiral bodies 23, 42.

Further, in this compressor, the drive bush 62 is
The counterweight 63 and the counterweight 63 are the circular irregularities 62 of both.
Since the fitting of b and 63c extends in the direction intersecting the sliding direction S of the drive bush 62, substantial counter-movement does not occur, and the counterweight 63 moves the movable scroll 4 through the drive bush 62. We do not support the offset of the eccentric moment received from.

Therefore, also in this compressor, the same operation and effect as those of the second embodiment can be exhibited. (Embodiment 4) An embodiment 4 embodying the invention of claims 3 and 4 will be described with reference to the drawings.

In this compressor, as shown in FIGS. 8 and 9, the drive bush 62 and the counterweight 63 are connected to each other by the uneven portion 6 orthogonal to the sliding direction S of the drive bush 62.
This is achieved by fitting 2c and 63d. In addition, the parallel sliding surface of the slide key 61 extends from the protruding end to the inner end 3 of the large diameter portion.
A cross-shaped oil groove 61a extending to 3a is engraved. Since other configurations are the same as those of the third embodiment, the same components are designated by the same reference numerals and the description thereof will be omitted.

In this compressor, the uneven portions 62c, 6c
Since 3d is formed in a linear shape, the same operation as that of the third embodiment can be exhibited although the manufacturing is easy. Further, in this compressor, since the oil groove 61a is formed on the parallel sliding surface of the slide key 61, it is extremely easy to manufacture. Since it can be slid appropriately, it is possible to more suitably absorb the minute difference between the spiral bodies 23 and 42 in the counter weight 63 and the drive bush 62.

Therefore, in this compressor, it is possible to achieve further excellent durability while realizing further reduction in manufacturing cost. In the third and fourth embodiments, the gaps between the slide holes 63a and 62a and the slide key 61 and the gap between the large diameter inner end 33a of the drive shaft 33 and the spot facing 63b are matched to each other, so that the counterweight 63 and Although the sliding range of the drive bush 62 is regulated, the sliding range is regulated by one of the gap between the slide holes 63a, 62a and the slide key 61 and the gap between the large diameter inner end 33a of the drive shaft 33 and the spot facing 63b. You can also

[0032]

As described above in detail, in the compressor of claims 1 to 4, the drive bush and the counter weight are coupled to each other such that they cannot rotate relative to each other, and the counter weight has the inner end of the large diameter portion of the drive shaft. Since the circular recess that is loosely fitted is formed, the torque transmitted between the drive bush and the counter weight and the drive shaft at the time of starting and stopping can be safely received.

Therefore, in the compressor according to claims 1 to 4,
Since no conventional rivet or the like that may be deformed is used, excellent durability can be exhibited. Further, in the compressor according to claims 2 and 4, the number of processing steps and the number of parts can be reduced because the number of rivets for fitting the drive bush and the counterweight is reduced.

Therefore, in the compressor of claims 2 and 4,
It is possible to reduce the manufacturing cost. In the compressors according to claims 1 to 5, the counterweight is a component independent of the drive shaft and the drive bush. Therefore, compared with the case where the drive shaft and the drive bush having a complicated shape are manufactured and assembled. , Easily manufactured and assembled.

[Brief description of drawings]

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

FIG. 2 is a cross-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 showing a main part of the compressor of the first embodiment.

FIG. 4 is a sectional view similar to FIG. 3, showing a main part of the compressor of the first embodiment and showing a state in which the drive shaft is rotated by a small angle from the state of FIG. 3.

FIG. 5 is a cross-sectional view of essential parts in a compressor according to a second embodiment.

FIG. 6 is a cross-sectional view of essential parts in a compressor according to a third embodiment.

FIG. 7 is a sectional view taken along the line BB of FIG. 6 showing a main part of the compressor according to a third embodiment.

FIG. 8 is a cross-sectional view of essential parts in a compressor according to a fourth embodiment.

FIG. 9 is a sectional view taken along the line CC of FIG. 8 showing 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 ... inner end of large diameter part 37 ... rotation preventing mechanism 36,52,62 ... drive bushes 35,53,63
... Counterweights 35b, 53b, 63b ... Counterbore (recesses) 52b, 53c, 62b, 63c, 62c, 63d ... Uneven portion 61 ... Slide key S ... Sliding direction

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tetsuo Yoshida, 2-chome, Toyota-cho, Kariya city, Aichi Stock company, Toyota Industries Corporation (72) Inventor Shinya Yamamoto, 2-chome, Toyota-cho, Kariya city, Aichi stock Incorporated company Toyota Industries Corporation (72) Inventor Masao Iguchi 2-chome Toyota Town, Kariya City, Aichi Stock Company Incorporated Toyota Industries Corporation (72) Inventor Kiyohiro Yamada 2-chome Toyota Town, Kariya City, Aichi Company Toyota Loom Works (72) Inventor Kunifumi Goto 2-chome Toyota Town, Kariya City, Aichi Stock Company Stock Company Toyota Loom Works (72) Inventor Tetsuya Yamaguchi 2-chome Toyota Town, Kariya City, Aichi Company Toyota Loom Works

Claims (4)

[Claims] 1. A fixed scroll, and a movable scroll which forms a compression chamber by meshing with the fixed scroll.
The movable scroll is rotatably supported via a bearing, and is fitted to the drive shaft having an eccentric pin projecting from the inner end of the large diameter portion and the eccentric pin. An eccentric drive bush that supports only the revolution and a counterweight that is arranged around the eccentric pin and absorbs the dynamic imbalance of the movable scroll, and the compression chamber is cooled by the revolution movement of the movable scroll. In a scroll compressor that sucks in gas and discharges by increasing the pressure of the refrigerant gas, the drive bush and the counter weight are coupled to each other such that they cannot rotate relative to each other, and the counter weight has a large diameter of the drive shaft. A scroll-type compressor characterized in that a circular concave portion is formed which is loosely fitted to the inner end of the portion to allow adjustment rotation. 2. The counterweight is provided by being fitted to the eccentric pin between the inner end of the large diameter portion of the drive shaft and the drive bush, and the drive bush and the counterweight are coupled to each other by the eccentric pin. It is achieved by fitting a circular uneven portion formed eccentrically with respect to
The scroll compressor described. 3. A fixed scroll, and a movable scroll which forms a compression chamber by meshing with the fixed scroll.
A drive shaft that is rotatably supported via a bearing, and has a slide key protruding from the inner end of the large diameter portion, and a slide key that is slidably mounted in a linear direction that is the reverse of the rotation direction of the drive shaft. And a drive bush that eccentrically supports the movable scroll via a bearing in cooperation with a rotation preventing mechanism to support only the revolution, and is disposed around the slide key to absorb the dynamic imbalance of the movable scroll. And a counterweight, wherein the orbiting movement of the movable scroll causes the compression chamber to suck the refrigerant gas and increase the pressure of the refrigerant gas to discharge the refrigerant gas, wherein the drive bush and the counterweight are opposed to each other. The counterweight is coupled non-rotatably, and 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 to allow adjustment linear sliding. A scroll type compressor characterized in that 4. The counter weight is provided by being fitted to the slide key between the inner end of the large diameter portion of the drive shaft and the drive bush, and the drive bush and the counter weight are coupled to each other by the drive bush. The scroll compressor according to claim 3, wherein the scroll compressor is achieved by fitting an uneven portion extending in a direction intersecting with a sliding direction of the scroll compressor.