JP2912818B2 - 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 used for a vehicle air conditioner, for example.
More specifically, the present invention relates to a lubrication structure for a crank mechanism that revolves a movable scroll member.

[0002]

2. Description of the Related Art As a scroll type compressor, FIG.
The following has been proposed. In this compressor,
The fixed scroll member 1 and the movable scroll member 8 are accommodated in the center housing 1d. A front housing 2 is joined and fixed to the front side of the housing 1d, and a large diameter portion 3a of a rotating shaft 3 is supported on the housing 2 via a radial bearing 4. A movable scroll member 8 is operatively connected to an eccentric shaft 5 provided at an inner end of the rotating shaft 3 via a bush 6 and a radial bearing 7. Housing 2 and movable scroll member 8
A rotation preventing mechanism K for preventing rotation of the orbiting scroll member and permitting revolving is interposed therebetween. further,
The eccentric shaft 5 is formed in a quadrangular prism shape, and the fitting hole 6a of the bush 6 has a parallel guide surface that reciprocates along the parallel guide surface 5a of the eccentric shaft 5. Therefore, when the movable scroll member 8 revolves in a state in which the rotation of the rotary shaft 3 is prevented from rotating around its own axis, the suction chamber 13
Space between the scroll members 1 and 8 (compression chamber)
The gas is sucked into P and compressed while its volume is reduced, and this gas is discharged to the discharge chamber 15. Further, since the bush 6 is reciprocated by the guide surface 5a of the eccentric shaft 5, as described in the embodiment of the present invention, the spiral portion 8b of the movable scroll member 8 with respect to the spiral portion 1b of the fixed scroll member 1 during the compression operation. Is properly maintained.

[0003]

In the conventional scroll type compressor, the front end face 6c of the bush 6 is in surface contact with the rear end face of the large diameter portion 3a of the rotary shaft 3, and the tip end of the eccentric shaft 5 is in contact with the front end face. A washer 21 for regulating the position of the bush 6 is locked by a circlip 22. For this reason, the sliding allowable space 23 between the eccentric shaft 5 and the bush 6 is a closed space, and the lubrication of the sliding surface between the eccentric shaft 5 and the bush 6 depends only on the accumulated oil in the space 23. Will be
There is a problem that sufficient lubrication of the sliding surface cannot be expected.

Further, since the space 24 formed between the rear end surface of the bush 6 and the movable scroll member 8 has a bag-like shape, the amount of oil passing through the gap G7 of the bearing 7 is extremely small. There was also a problem that lubrication of No. 7 could not be expected.

The eccentric shaft 5 is formed in a cylindrical shape, and a bush 6 is fitted to the bush 6 so as to be relatively rotatable. Since there is no path for supplying gas to the moving surface, lubrication of the sliding surface poses a problem.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll compressor capable of improving the lubricity of a crank mechanism that revolves in a state where the movable scroll member is prevented from rotating, while solving the above-mentioned problems in the prior art. To provide.

[0007]

According to a first aspect of the present invention, there is provided a housing having a suction port and a discharge port, a fixed scroll member having a spiral portion formed on a substrate and fixed inside the housing, and a substrate. A movable scroll member having a spiral portion formed thereon and being fitted to the fixed scroll member so as to be offset from the center, a rotating shaft supported by the housing via a first radial bearing, An eccentric shaft that is eccentrically connected to the inner end of the shaft and is formed in a quadrangular prism shape, a bush fitted on the outer periphery of the eccentric shaft, and a movable scroll on the outer peripheral surface of the bush via a second radial bearing The boss portion of the member is fitted so as to be relatively rotatable, a rotation preventing mechanism that allows only the revolution of the movable scroll member and prevents rotation, and the bush. And a balance weight for compensating for dynamic imbalance during the revolving motion of the movable scroll member. The hermetic motion of the movable scroll member causes a closed compression chamber between the movable scroll member and the fixed scroll member to become a suction chamber. In the scroll compressor, which is moved toward the center of the spiral part while reducing the volume of gas taken in from the scroll type and discharges the compressed gas to the discharge chamber, the outer peripheral surface of the eccentric shaft and the inner peripheral surface of the bush A lubrication passage extending in the axial direction formed between the lubrication passage and the space allowing the reciprocal sliding of the eccentric shaft and the bush, and a lubrication passage between the lubrication passage and the rear end surface of the bush and the inner top surface of the boss portion. A first communication passage communicating with the bag-shaped space formed in the second bearing, the bag-shaped space being connected to a gap of the second radial bearing, And a second communication passage formed in the radial direction on a surface facing the second communication passage and communicating the lubrication passage with the suction chamber, and formed annularly with respect to an inner peripheral surface of a fitting hole of the bush for fitting the eccentric shaft. A notch recess that is open to the inner end surface of the rotating shaft and communicates with the lubrication passage and communicates with the inner end of the second communication passage, and a fitting hole of a bush that fits the eccentric shaft has an eccentric shaft. The gist of the present invention is a scroll compressor having a parallel guide surface that reciprocates in the radial direction along the formed parallel guide surface.

According to a second aspect of the present invention, in the first aspect, a groove for increasing the volume of the lubrication passage is provided in at least one of the outer peripheral surface of the eccentric shaft and the inner peripheral surface of the fitting hole of the bush in the axial direction. ing.

[0009]

According to the first aspect of the invention, the refrigerant gas in the suction chamber is taken into the closed compression chamber formed by the fixed and movable scroll members by the revolving motion of the movable scroll member, and the compression chamber is located at the center. The gas is compressed while decreasing the volume as it goes.

[0010] The lubrication passage formed between the eccentric shaft and the bush is communicated with the bag-like space through the first communication passage, and is communicated with the suction chamber through the second communication passage. For this reason, during the operation of the compressor, the gap between the suction chamber and the second bearing, the bag-shaped space, the first communication passage, the lubrication passage, and the second
A gas circulation path is formed through the communication passage to the suction chamber,
A gas containing mist-like oil is supplied to the sliding interface between the eccentric shaft and the bush, and the gap between the bearings and the lubricating properties of the sliding interface are improved.

During operation of the compressor, the parallel guide surface of the bush slides along the parallel guide surface of the eccentric shaft, and the spiral portion of the movable scroll member follows the scroll shape of the spiral portion of the fixed scroll member. Orbiting. At this time, since the gas containing oil is supplied from the suction chamber to the sliding allowable space as the lubricating passage, the lubricating property of the sliding interface is improved.

Further, since the cutout recess is formed in an annular shape on the inner peripheral surface of the fitting hole of the bush, the length of the lubrication passage is shortened, and the effect of circulating oil-containing gas is further improved. For this reason, the gas which has entered the notch recess from the lubrication passage is efficiently supplied also to the sliding contact interface between the rotary shaft and the bush.
In addition, by providing the cutout recess, the processing area of the parallel guide surface, which requires relatively high precision processing, is reduced, so that the processing is facilitated.

Further, according to the second aspect of the present invention, since the groove for increasing the volume of the lubrication passage is provided in the second aspect,
The flow rate of the gas in the lubrication passage increases, and more oil is supplied to the bearing and the sliding interface, thereby improving the lubricity of the oil.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described below with reference to FIGS. As shown in FIG. 1, a front housing 2 is joined and fixed to a fixed scroll member 1 also serving as a center housing 1d. A large-diameter portion 3a of the rotating shaft 3 is supported by a first radial bearing 4 in a center hole of the front housing 2, and an eccentric shaft 5 having a quadrangular prism shape as shown in FIG. It is formed integrally. The eccentric shaft 5 has a square cylindrical fitting hole 6
A bush 6 having a is rotatably supported integrally with the eccentric shaft 5. A movable scroll member 8 is rotatably supported on the bush 6 via a second radial bearing 7 so as to be opposed to and joined to the fixed scroll member 1. The scroll members 1 and 8 are composed of substrates 1a and 8a and spiral portions 1b and 8b formed integrally with the substrates at right angles. A bush 6 and a second bearing 7 are fitted on the back surface of the substrate 8a of the movable scroll member 8. The boss portion 8c is integrally formed. The scroll substrates 1a, 8a and the spiral portions 1b, 8b form a compression chamber P for compressing the refrigerant gas while decreasing the volume from the outside toward the center. The bush 6 is integrally formed with a balance weight 9 for compensating for a dynamic imbalance during the revolving motion of the movable scroll member 8.

Between the rear surface (movable-side pressure receiving wall) 8d of the movable scroll substrate 8a and the inner side wall (fixed-side pressure receiving wall) 2a of the front housing 2, the movable scroll member 8 rotates around its own axis (rotation). ), And a rotation preventing mechanism K1 for intermittently permitting a circular orbital movement (revolution) of a predetermined radius around the central axis of the rotating shaft 3 is provided. That is, a plurality of (four in this embodiment, as shown in FIG. 4) fitting holes 2b are formed in the fixed-side pressure receiving wall 2a. or,
A plurality of fitting holes 8e are formed in the movable-side pressure receiving wall 8d so as to correspond to the fitting holes 2b. Further, the fixed-side pressure receiving wall 2
and a movable-side pressure receiving wall 8d, an annular rotation-preventing ring 11 is interposed therebetween, and the ring 11 has a plurality of rotation-preventing pins 12 loosely engaged with the opposed fitting holes 2b and 8e, respectively. Are supported through. On the front and rear side surfaces of the ring 11, pressure receiving element portions 11a for receiving the reaction force during the compression operation of the refrigerant gas in the compression chamber P from the movable side pressure receiving wall 8d to the fixed side pressure receiving wall 2a are equiangularly arranged at a plurality of locations. And are integrally formed.

A suction chamber 13 is formed between the movable scroll member 8 and the inner peripheral surface of the center housing 1d. Refrigerant gas is introduced into the suction chamber 13 from a suction flange (suction port) 1e formed in the center housing 1d. The gas in the suction chamber 13 passes through the gap of the rotation preventing mechanism K1 and accommodates a crank mechanism K2 for revolving the movable scroll member 8 including the rotary shaft 3, the eccentric shaft 5, the bush 6, the second bearing 7, and the like. It communicates with the room R.

A rear housing 14 is joined and fixed to the rear end surface of the fixed scroll member 1, and the substrate 1a
And a discharge chamber 15 is formed. A discharge port 1c is formed in the fixed scroll substrate 1a, and a discharge valve 16 for opening and closing the discharge port 1c is provided in the discharge chamber 15. A discharge flange (discharge port) 14 a is formed on the outer periphery of the rear housing 14.

As shown in FIG. 1, the small diameter portion 3b of the rotating shaft 3
A shaft seal mechanism 17 is provided between the first housing 4 and the shaft hole, and a shaft seal chamber 18 is formed between the seal mechanism 17 and the first bearing 4. The seal chamber 18 communicates with the crank chamber R via a gap G4 between the first bearings 4. Then, the gas in the crank chamber R passes through the gap G4 and the seal chamber 1
8 to lubricate the seal mechanism 17.

Next, the lubrication structure of the crank mechanism K2 of the movable scroll member 8, which is a main part of the present invention, will be described. As shown in FIGS. 2 and 3, the eccentric shaft 5 is formed in a quadrangular prism shape, and its parallel guide surfaces 5a, 5a
Guide surfaces 6b, 6 of the square cylindrical fitting hole 6a
b is reciprocally slidable in the radial direction of the eccentric shaft 5. The front end face 6c of the bush 6 is in sliding contact with the rear end face 3c of the large diameter portion 3a of the rotating shaft 3. The tip of the eccentric shaft 5 is the rear end face 6 of the bush 6.
d, and a washer 21 is fitted to the tip. Further, a locking groove 5b is formed on the outer periphery of the distal end of the eccentric shaft 5, and a circlip 22 is locked in the groove to prevent the bush 6 from moving on the eccentric shaft 5 in the axial direction together with the washer 21. Like that.

The bush 6 is provided with the eccentric shaft 5 as described above.
Is reciprocally slid in the radial direction along the parallel guide surface 5a.
In order to allow this reciprocating sliding, the parallel guide surface 5a of the eccentric shaft 5
Are formed at both ends thereof with sliding allowable spaces 23 as lubricating passages. Also, the rear end face 3 of the large diameter portion 3a of the rotating shaft 3
c and the front end face 6 c of the bush 6 are in sliding contact with each other, and a washer 21 is locked to the tip of the eccentric shaft 5 by a circlip 22. For this reason, the sliding allowable space 23 is in a state where communication with the outside is shut off, and insufficient lubrication is likely to occur. Therefore, in the first embodiment, as shown in FIG. 3, the notch recesses 21b are formed at the four corners of the fitting holes 21a of the washer 21 in correspondence with the sliding allowable spaces 23.
Is formed. A bag-shaped space 24 is formed between the rear end surface 6d of the bush 6 and the inner top surface of the boss 8c. The first communication passage 2 which connects the sliding allowable space 23 and the bag-shaped space 24 to each other by a gap between the parallel guide surface 5a of the eccentric shaft 5 and the circlip 22 and the notch recess 21b.
5 are formed.

Further, a gap 26 is formed between the rear end surface of the bush 6 and the inner top surface of the boss 8c as shown in FIG. The second bearing 7 communicates with the crank chamber R through a gap G7.

Further, the front end face 6c of the bush 6
A notched recess 6e communicating with the space 23 is formed. Also, the rear end face 3c of the large diameter portion 3a of the rotary shaft 3
The second communication passage 27 is formed by forming a recess 3d communicating with the notch recess 6e. As shown in FIG. 6, the second communication passage 27 is formed so as to be wider toward the outer peripheral surface of the large diameter portion 3a.
The outflow of gas to the air is promoted.

The inner peripheral surface 4 of the fitting hole 6a of the bush 6
A plurality of relief grooves 6f are formed for one corner.
Accordingly, a gas circulation path from the crank chamber R to the crank chamber R via the gap G7, the gap 26, the bag-shaped space 24, the first communication passage 25, the space 23, and the second communication passage 27 of the second bearing 7 is formed. Is formed.

Next, the operation of the scroll compressor configured as described above will be described. Now, when the rotary shaft 3 is rotated by the power of the engine or the like and the eccentric shaft 5 revolves, the bush 6 has a predetermined radius around the central axis O1 of the rotary shaft 3, that is, the axis O1 and the central axis O2 of the bush 6. Distance L
Revolves along a circular orbit with a radius of. Then, the movable scroll member 8 revolves around the central axis O1 of the rotating shaft 3 in a state where the rotation is prevented by the rotation preventing mechanism K1. That is, the plurality of rotation prevention pins 12 of the rotation prevention mechanism K1
Is fitted in the fixed side fitting hole 2b, so that the movable scroll member 8 is prevented from rotating. Further, since each pin 12 is loosely fitted in both fitting holes 2b and 8e, the movable scroll member 8 has a diameter of 2 (D-d) where D is the diameter of the holes 2b and 8e and d is the diameter of the pin 12. ) Is the maximum orbital radius (same as the maximum value of the distance L).
Due to the revolving motion of the movable scroll member 8, the refrigerant gas introduced into the suction chamber 13 from the external refrigerant pipe and the suction flange 1e flows into the compression chamber P between the scroll members 1 and 8. The compression chamber P decreases in volume as the movable scroll member 8 revolves, and the scroll portions 1b,
8b converge toward the center. The refrigerant gas compressed by the reduction in the volume of the compression chamber P is discharged from the discharge port 1c into the discharge chamber 15. The refrigerant gas discharged into the discharge chamber 15 is sent from the discharge flange 14a to an external refrigerant pipe.

During the compression operation, the compression reaction force of the refrigerant gas in the compression chamber P acts on the movable scroll member 8. This reaction force is applied to the pressure receiving element portion 1 of the ring 11 from the movable side pressure receiving wall 8d.
It is received by the fixed-side pressure receiving wall 2a via 1a.

During the operation of compressing the refrigerant gas, the outer peripheral surface of the spiral portion 8b of the movable scroll member 8 is rotated by the centrifugal force caused by the revolving motion.
Is in sliding contact with the inner peripheral surface of The sliding portion moves as a seal portion of the compression chamber P following the shape of the fixed spiral portion 1b.
Since the engagement of the two spiral portions 1b and 8b is not accurate due to processing and assembly errors, the movable spiral portion 8b is fixed to the fixed spiral portion 1b.
Displaced in the radial direction with respect to b. This displacement is also caused by liquid compression. The displacement of the movable spiral portion 8b is determined by a predetermined stroke, that is, the space 23, because the bush 6 has a fitting structure in which the bush 6 can reciprocate in the radial direction with respect to the eccentric shaft 5.
Is allowed within the width of Therefore, lubrication of the sliding interface between the eccentric shaft 5 and the bush 6 and the sliding interface between the rear end surface 3c of the large diameter portion 3a of the rotary shaft 3 and the front end surface 6c of the bush 6 are required.

In the first embodiment, the washer 21 is provided with a first communication passage 25 for communicating the space 23 with the bag-shaped space 24, and the large diameter portion 3 a of the rotating shaft 3 is provided with a space 2.
3. A second communication passage 27 is provided for communicating the notch recess 6e with the crank chamber R side. Therefore, the gas from the crank chamber R to the crank chamber R via the gap G7, the gap 26, the bag-shaped space 24, the first communication passage 25, the sliding allowable space 23, the notch space 6e, and the second communication passage 27 of the bearing 7 is provided. Is formed. Also, the second communication passage 27 is revolved by the revolving motion of the movable scroll member 8. At this time, in FIG. 2, the gas in the second communication passage 27 flows in a direction of jumping outward due to the centrifugal force, so that the gas flows in the circulation path as shown by the arrow in FIG. 2. Therefore, gas containing mist-like oil is supplied to the sliding interface between the bearing 7 or the eccentric shaft 5 and the parallel guide surfaces 5a and 6b of the bush 6, the sliding interface between the large diameter portion 3a and the bush 6, and the like. The lubrication is performed so that the durability of the crank mechanism K2 of the movable scroll member 8 can be improved.

Further, in this embodiment, since the notch recess 6e is provided, the distance of the slide allowable space 23 having a small passage area is shortened, and the circulation of gas is promoted. For this reason, the lubricating property of each sliding contact interface is further improved, and the durability of the crank mechanism K2 can be further improved. Further, in this embodiment, since the notch recess 6e is provided, the processing area of the parallel guide surface 6b of the fitting hole 6a of the bush 6 is reduced, and the processing can be easily performed.

Further, since a plurality of relief grooves 6f are provided, the volume of the sliding allowable space 23 can be increased and the flow rate of gas can be increased, thereby further improving the lubricating property of each sliding interface. In addition, the durability of the crank mechanism K2 can be further improved.

Further, in this embodiment, the lubrication of the crank mechanism K2 is improved by the amount of the concave portion 3d (the second communication passage 27) formed so as to become wider toward the outer peripheral surface of the large diameter portion 3a. Can be.

The present invention is not limited to the above embodiment, but can be embodied as follows. (1) As shown in FIG. 7, the concave portion 3d is formed so as to be inclined so that gas can be introduced into the cutout concave portion 6e in the direction of rotation of the rotating shaft 3. This embodiment is different from the first embodiment. In comparison, the gas flow direction of the gas circulation path is reversed, but the lubrication of the crank mechanism K2 is performed in the same manner as in the first embodiment, and the durability thereof can be improved. In FIG. 7, reference numeral 5c denotes a relief groove provided on the outer peripheral surface of the eccentric shaft 5. The escape groove 5c has the same effect as the escape groove 5f.

The technical ideas other than the claims that can be grasped from the above embodiment will be described below together with their effects. The space 23 and the shaft seal chamber 18 formed on the front side of the bearing 4 supporting the large diameter portion 3a communicate with the large diameter portion 3a of the rotating shaft 3 according to any one of claims 1 to 2. Scroll compressor provided with the second communication passage 27 as described above.

In this compressor, the lubricating properties of the shaft seal mechanism 17 and the bearing 4 can be improved in addition to the effects of the invention described in claim 1 or 2.

Further, in this specification, the first communication passage 25 is a passage connecting the space 23 and the bag-shaped space 24, and the notch recess 21b formed in the washer 21 is used.
In addition, a groove formed in the bush 6 and a groove or passage formed in the eccentric shaft 5 may be used.

[0035]

As described above in detail, the invention according to claim 1 or 2 can improve the lubricity of the crank mechanism that revolves while the movable scroll member is prevented from rotating.

According to the first aspect of the present invention, since the cutout recess is formed in an annular shape on the inner peripheral surface of the fitting hole of the bush, the lubricity of the crank mechanism can be further improved. Further, by providing the cutout recess, the processing area of the parallel guide surface on the bush side, which requires relatively high precision processing, is reduced, so that the processing can be easily performed. Further, by providing the second communication path, a gas circulation path to the suction chamber via the second communication path can be formed.

According to the second aspect of the present invention, since the groove for increasing the volume of the sliding allowable space of the bush is provided in the first aspect, the flow rate of the gas is increased, and the lubricity of the crank mechanism can be further improved. it can.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part of the first embodiment.

FIG. 3 is an exploded perspective view of a rotating shaft, a bush, and a balance weight according to the first embodiment.

FIG. 4 is a sectional view of a main part of the first embodiment.

FIG. 5 is a cross-sectional view of the scroll member of the first embodiment.

FIG. 6 is a sectional view of a main part of the first embodiment.

FIG. 7 is a partial sectional view showing another example of the present invention.

FIG. 8 is a longitudinal sectional view of a conventional scroll compressor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Fixed scroll member, 1a ... Substrate, 1b ... Spiral part,
1d: center housing, 2: front housing, 3
... Rotary shaft, 4 ... First radial bearing, 5 ... Eccentric shaft,
5a: parallel guide surface, 5c: relief groove, 6: bush, 6a
... fitting holes, 6b ... parallel guide surfaces, 6e ... cutout recesses, 6f ...
Relief groove, 6g fitting protrusion, 6h groove forming the second communication passage 27, 7 second radial bearing, 8 movable scroll member, 8a substrate, 8b spiral part, 8c boss part,
9 ... balance weight, 13 ... suction chamber, 14 ... rear housing, 15 ... discharge chamber, 21 ... washer, 21a ... fitting hole, 21b ... cutout recess, 22 ... circlip, 23 ...
Sliding allowable space as lubrication passage, 23 '... lubrication passage, 2
4 ... bag-shaped space, 25 ... first communication path, 26 ... gap, 27 ...
Second communication path, G4: gap between bearings 4, G7: gap between bearings 7, K1: anti-rotation mechanism, P: compression chamber.

──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Tetsuhiko Fukanuma 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside the Toyota Industries Corporation (72) Inventor Shinya Yamamoto 2-1-1, Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (56) References Japanese Utility Model Sho 59-15884 (JP, U) Japanese Utility Model Utility Model Hei 4-37803 (JP, U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 18 / 02 311

Claims (2)

(57) [Claims] 1. A housing having a suction port and a discharge port, a spiral part formed on a substrate, a fixed scroll member fixed inside the housing, and a spiral part formed on the substrate, A movable scroll member incorporated so as to be engaged with the fixed scroll member at a shifted center, a rotating shaft supported by the housing via a first radial bearing, and eccentrically coupled to an inner end of the rotating shaft ; Square pillar shape
The formed eccentric shaft, a bush fitted on the outer periphery of the eccentric shaft, and a boss portion of a movable scroll member fitted on the outer peripheral surface of the bush via a second radial bearing so as to be relatively rotatable. And a rotation preventing mechanism that allows only the revolution of the movable scroll member and prevents rotation, and a balance weight that is provided on the bush and compensates for dynamic imbalance during the revolving motion of the movable scroll member, Due to the revolving motion of the movable scroll member, the sealed compression chamber between the movable scroll member and the fixed scroll member is moved toward the center of the spiral portion while reducing the volume of the gas taken in from the suction chamber, and the compressed gas is removed. in the scroll compressor adapted to discharge to the discharge chamber, extending in the axial direction which is formed between the outer surface and the inner peripheral surface of the bush of the eccentric shaft Huh reciprocating sliding of the eccentric shaft and the bushing
A lubricating passage which is a space to accommodate; a first communicating passage communicating between the lubricating passage, a rear end surface of the bush, and an inner top surface of the boss portion; and that communicates with the gap of the second radial bearing are each of the bushing or the rotary shaft
It is formed in its radial direction opposed surfaces, and a second communication passage for communicating the lubricating passage and the suction chamber, the inner peripheral surface of the fitting hole of the bush to be fitted the eccentric shaft to
Formed in an annular shape, opening to the inner end face of the rotating shaft, and
The lubrication passage communicates with the inner end of the second communication passage.
The cut-out recess passed through and the fitting hole of the bush for fitting the eccentric shaft are formed on the eccentric shaft.
Parallel plan that slides back and forth in the radial direction along the parallel guide surface
A scroll compressor with an inner surface . 2. A scroll type compressor according to claim 1 , wherein a groove for increasing the volume of said lubrication passage is provided in at least one of an outer peripheral surface of an eccentric shaft and an inner peripheral surface of a fitting hole of a bush in an axial direction.