US20200088193A1

US20200088193A1 - Co-rotating scroll compressor

Info

Publication number: US20200088193A1
Application number: US16/615,478
Authority: US
Inventors: Takuma YAMASHITA; Takahide Ito; Keita Kitaguchi; Makoto Takeuchi; Hirofumi Hirata
Original assignee: Mitsubishi Heavy Industries Ltd
Current assignee: Mitsubishi Heavy Industries Ltd
Priority date: 2017-08-25
Filing date: 2018-08-24
Publication date: 2020-03-19
Also published as: EP3613985A1; WO2019039575A1; JPWO2019039575A1; EP3613985A4; JP6804655B2; CN110959072A

Abstract

This co-rotating scroll compressor is provided with: a first side plate (27) which is arranged on the side of a drive-side rotational axis direction (CL1) with respect to a drive-side scroll member (70) and a driven-side scroll member (90), a second side plate (30) fixed at a predetermined gap in the direction of the drive-side rotational axis (CL1) with respect to the first side plate (27), and a center plate (20) arranged between the first side plate (27) and the second side plate (30). The first side plate (27) is fixed to the driven-side scroll member (90), and the center plate (20) is fixed to the drive-side scroll member (70). A synchronization drive mechanism equipped with a crank pin (15) is disposed between the first side plate (27) and second side plate (30) and the center plate (20).

Description

TECHNICAL FIELD

The present invention relates to a co-rotating scroll compressor.

BACKGROUND ART

A co-rotating scroll compressor is known in the related art (see PTL 1). The co-rotating scroll compressor is provided with a drive-side scroll and a driven-side scroll rotating synchronously with the drive-side scroll. A driven shaft supporting the rotation of the driven-side scroll is offset by a turning radius with respect to a drive shaft rotating the drive-side scroll. As a result, the drive shaft and the driven shaft are rotated in the same direction and at the same angular velocity.

CITATION LIST

Patent Literature

[PTL 1] Japanese Patent No. 5443132

SUMMARY OF INVENTION

Technical Problem

In the co-rotating scroll compressor, a synchronization drive mechanism transmitting a drive force from a drive-side scroll member to a driven-side scroll member is used such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity. Although a mechanism using a crank pin or a pin ring is conceivable as the synchronization drive mechanism, the life of the synchronization drive mechanism may be shortened due to compression heat transmission from the scroll member. A decrease in the life of the synchronization drive mechanism needs to be prevented particularly in a case where a lubricant is used.
When the synchronization drive mechanism is adopted between the two members, that is, the drive-side scroll member and the driven-side scroll member, a load is applied to the synchronization drive mechanism at two places, which may result in moment generation around the synchronization drive mechanism and a decrease in the life of the synchronization drive mechanism.
In a case where a pin ring or a crank pin provided with a rolling bearing is used as the synchronization drive mechanism, the lubricant that is enclosed in the rolling bearing may leak to the outside due to a centrifugal force, and then a decrease in bearing life may result from insufficient lubrication. In addition, the lubricant leakage may result in mixing into a compressed fluid and fluid contamination.
In a case where the crank pin provided with the rolling bearing is used as the synchronization drive mechanism, it is necessary to provide at least two rolling bearings supporting crank pin rotation, which leads to an increase in cost.
In a case where the crank pin provided with the rolling bearing is used as the synchronization drive mechanism, the tolerance of the crank pin, the tolerance of the hole into which the rolling bearing is inserted, or the like may lead to internal force generation in the crank pin and a decrease in the life of the synchronization drive mechanism. In a case where cutting is performed with the crank pin integrated in particular, a crank pin machining error is likely to occur and the internal force that is generated in the crank pin may increase.
The present invention has been made in view of such circumstances, and an object of the present invention is to provide a co-rotating scroll compressor with which the life of a synchronization drive mechanism can be extended.
An object of the present invention is to provide a co-rotating scroll compressor with which the cost of a synchronization drive mechanism can be reduced.
An object of the present invention is to provide a co-rotating scroll compressor with which the life of a synchronization drive mechanism that is a crank pin mechanism can be extended.

Solution to Problem

A co-rotating scroll compressor according to an aspect of the present invention includes a drive-side scroll member driven to rotate around a rotational axis by a drive unit and having a spiral drive-side wall body disposed on a drive-side end plate, a driven-side scroll member in which a spiral driven-side wall body corresponding to the drive-side wall body is disposed on a driven-side end plate and the driven-side wall body meshes with the drive-side wall body to form a compression space, a synchronization drive mechanism transmitting a drive force of the drive unit to the driven-side scroll member such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity, a first side plate disposed on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member, a second side plate fixed at a predetermined gap in the rotational axis direction with respect to the first side plate, and a center plate disposed between the first side plate and the second side plate. The first side plate is fixed to one of the drive-side scroll member and the driven-side scroll member. The center plate is fixed to the other of the drive-side scroll member and the driven-side scroll member. The synchronization drive mechanism is provided between the first and second side plates and the center plate.
The compression space is formed by the drive-side wall body disposed on the drive-side end plate of the drive-side scroll member and the driven-side wall body of the driven-side scroll member meshing with each other. The drive-side scroll member is driven to rotate by the drive unit and the drive force is transmitted to the driven-side scroll member via the synchronization drive mechanism. As a result, the driven-side scroll member rotates and performs a rotating motion in the same direction and at the same angular velocity with respect to the drive-side scroll member. Provided in this manner is the co-rotating scroll compressor in which both the drive-side scroll member and the driven-side scroll member rotate.
The first side plate and the second side plate are provided on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member and the center plate is provided between the side plates. The synchronization drive mechanism is provided between both side plates and the center plate. Since the side plates and the center plate as members separate from both scroll members are provided with the synchronization drive mechanisms as described above, heating attributable to the compression heat from the scroll members can be decreased and the life of the synchronization drive mechanisms can be extended.
A load is applied to the synchronization drive mechanism from the center plate and the side plates on both sides thereof, and thus the moment around the center plate can be canceled and the life of the synchronization drive mechanisms can be extended.
The synchronization drive mechanisms are disposed by both side plates and the center plate being provided on the rotational axis direction side, and thus diameter reduction can be achieved as compared with a case where a synchronization drive mechanism is provided on radial direction sides of the scroll members.
In the co-rotating scroll compressor according to an aspect of the present invention, the synchronization drive mechanism is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion and a crank pin end portion rolling bearing provided between both end portions of the eccentric shaft portion and the first and second side plates and an urging member urging an inner ring of the crank pin end portion rolling bearing toward a leading edge of the eccentric shaft portion in the eccentric axis direction is provided between the inner ring and the eccentric shaft portion.
The crank pin and the crank pin end portion rolling bearing constitute the synchronization drive mechanism and the crank pin end portion rolling bearing rotatably and pivotally supports both end portions of the crank pin with both side plates. The urging member urging the inner ring toward the leading edge of the eccentric shaft portion in the eccentric axis direction is provided between the inner ring of the crank pin end portion rolling bearing and the eccentric shaft portion of the crank pin. The urging member urges the inner ring of the crank pin end portion rolling bearing toward the leading edge, and thus an outer ring is pressed against the side plate via the rolling body of the crank pin end portion rolling bearing. As a result, the crank pin end portion rolling bearing is put into a state where a preload is applied between the eccentric bearing of the crank pin and the side plate, it is possible to prevent slipping between the rolling body and the inner ring and slipping between the inner ring and the eccentric shaft portion, and the life of the synchronization drive mechanism can be extended.
An O-ring or the like is used as the urging member.
In the co-rotating scroll compressor according to an aspect of the present invention, the synchronization drive mechanism is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion and a crank pin end portion rolling bearing provided between both end portions of the eccentric shaft portion and the first and second side plates and a preload is applied to the crank pin end portion rolling bearing in the eccentric axis direction by a gap between the first side plate and the second side plate.
The crank pin and the crank pin end portion rolling bearing constitute the synchronization drive mechanism and the crank pin end portion rolling bearing rotatably and pivotally supports both end portions of the crank pin with both side plates. A preload is applied to the crank pin end portion rolling bearing in the eccentric axis direction by the gap between the first side plate and the second side plate. As a result, it is possible to prevent slipping between the rolling body of the crank pin end portion rolling bearing and the inner ring and slipping between the inner ring and the eccentric shaft portion and the life of the synchronization drive mechanism can be extended.
By a specific preload application method, the gap between the side plates is narrowed when the second side plate is fastened to the first side plate. In other words, the gap determined by both side plates being fastened is kept smaller than the gap between both side plates determined by the crank pin end portion rolling bearing and the crank pin of the synchronization drive mechanism.
In the co-rotating scroll compressor according to an aspect of the present invention, the synchronization drive mechanism is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion and a crank pin end portion rolling bearing provided between both end portions of the eccentric shaft portion and the first and second side plates and an elastic body is provided between an inner peripheral surface of an inner ring of the crank pin end portion rolling bearing and an outer peripheral surface of the eccentric shaft portion.
The crank pin and the crank pin end portion rolling bearing constitute the synchronization drive mechanism and the crank pin end portion rolling bearing rotatably and pivotally supports both end portions of the crank pin with both side plates. The elastic body is provided between the inner peripheral surface of the inner ring of the crank pin end portion rolling bearing and the outer peripheral surface of the eccentric shaft portion. As a result, a reaction force is generated by the elastic body sandwiched between the inner ring and the eccentric shaft portion being deformed, slipping between the eccentric shaft portion and the inner ring can be prevented, and the life of the synchronization drive mechanism can be extended.
In the co-rotating scroll compressor according to an aspect of the present invention, among a fixing portion of the first side plate which is fixed to one of the drive-side scroll member and the driven-side scroll member and a fixing portion of the center plate which is fixed to the other of the drive-side scroll member and the driven-side scroll member, the fixing portion positioned on a radial inner side of a center of the scroll member has a structure in which a resin portion is interposed, and the fixing portion positioned on a radial outer side of the center of the scroll member has a structure using a metal portion without resin portion interposition.
The structure in which the resin portion is interposed is because the temperature of the fixing portion positioned on the radial inner side of the center of the scroll member tends to rise due to compression heat. As a result, it is possible to achieve life extension by suppressing a rise in the temperature of the synchronization drive mechanism.
The metallic structure without resin portion interposition is because a rise in temperature attributable to compression heat has little effect on the fixing portion positioned radially outward of the center of the scroll member. As a result, the fixing portion can be accurately assembled by means of metal, and thus the synchronization drive mechanism can be accurately positioned, phase shift reduction can be achieved between the drive-side scroll member and the driven-side scroll member, and compression performance improvement can be achieved.
The co-rotating scroll compressor according to an aspect of the present invention includes a drive-side scroll member driven to rotate around a rotational axis by a drive unit and having a spiral drive-side wall body disposed on a drive-side end plate, a driven-side scroll member in which a spiral driven-side wall body corresponding to the drive-side wall body is disposed on a driven-side end plate and the driven-side wall body meshes with the drive-side wall body to form a compression space, a synchronization drive mechanism transmitting a drive force to the driven-side scroll member such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity, a first side plate disposed on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member, a second side plate fixed at a predetermined gap in the rotational axis direction with respect to the first side plate, and a center plate disposed between the first side plate and the second side plate. The first side plate is fixed to one of the drive-side scroll member and the driven-side scroll member. The center plate is fixed to the other of the drive-side scroll member and the driven-side scroll member. The synchronization drive mechanism is provided between the first and second side plates and the center plate. A peripheral wall portion surrounding an outer peripheral side of the center plate is provided between the first side plate and the second side plate.
The compression space is formed by the drive-side wall body disposed on the drive-side end plate of the drive-side scroll member and the driven-side wall body of the driven-side scroll member meshing with each other. The drive-side scroll member is driven to rotate by the drive unit and the drive force is transmitted to the driven-side scroll member via the synchronization drive mechanism. As a result, the driven-side scroll member rotates and performs a rotating motion in the same direction and at the same angular velocity with respect to the drive-side scroll member. Provided in this manner is the co-rotating scroll compressor in which both the drive-side scroll member and the driven-side scroll member rotate.
The first side plate and the second side plate are provided on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member and the center plate is provided between the side plates. The synchronization drive mechanism is provided between both side plates and the center plate. The peripheral wall portion surrounding the outer peripheral side of the center plate is provided between the first side plate and the second side plate. As a result, even when the lubricant supplied to the synchronization drive mechanism is moved to the outer peripheral side by a centrifugal force, the lubricant can be held on the inner peripheral side of the peripheral wall portion, and thus an insufficient lubrication of the synchronization drive mechanism can be avoided and life extension can be achieved.
Usable as the synchronization drive mechanism is, for example, a crank mechanism provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion and a crank pin end portion rolling bearing provided between both end portions of the eccentric shaft portion and the first and second side plates. The rolling bearing is supplied with a lubricant.
The co-rotating scroll compressor according to an aspect of the present invention further includes a drive shaft portion rotating around the rotational axis and connected between the drive-side end plate and the drive unit. The center plate is fixed to the drive shaft portion. A hole portion for the first side plate through which the drive shaft portion passes is formed in the first side plate. A hole portion for the second side plate through which the drive shaft portion passes is formed in the second side plate. A first seal member is provided between the hole portion for the first side plate and the drive shaft portion and/or between the hole portion for the second side plate and the drive shaft portion.
The drive shaft portion is provided between the drive-side end plate and the drive unit and the center plate is fixed to the drive shaft portion. As a result, a drive force is transmitted from the drive unit to the drive-side scroll member via the center plate.
The hole portions through which the drive shaft portion passes are respectively provided in the first side plate and the second side plate. As a result, a gap is inevitably formed between both side plates and the drive shaft portion. The first seal member is provided so as to seal the gap. As a result, it is possible to prevent lubricant leakage from the space between both side plates and the drive shaft portion.
A boots seal, a labyrinth seal, or the like can be adopted as the first seal member.
The co-rotating scroll compressor according to an aspect of the present invention further includes a drive shaft portion rotating around the rotational axis and connected between the drive-side end plate and the drive unit. The center plate is fixed to the drive shaft portion. A hole portion for the first side plate through which the drive shaft portion passes is formed in the first side plate. A hole portion for the second side plate through which the drive shaft portion passes is formed in the second side plate. A second seal member is provided between the first side plate and the center plate and/or between the second side plate and the center plate.
The drive shaft portion is provided between the drive-side end plate and the drive unit and the center plate is fixed to the drive shaft portion. As a result, a drive force is transmitted from the drive unit to the drive-side scroll member via the center plate.
The hole portions through which the drive shaft portion passes are respectively provided in the first side plate and the second side plate. As a result, a gap is inevitably formed between both side plates and the drive shaft portion. The second seal member is provided between both side plates and the center plate. As a result, it is possible to prevent lubricant leakage from the space between both side plates and the drive shaft portion.
Adoptable as the second seal member is, for example, a tip seal inserted in a circumferential groove formed in each side plate or the center plate.
In the co-rotating scroll compressor according to an aspect of the present invention, the first side plate is fixed to the drive-side wall body on an outer peripheral side, the second side plate is fixed to the first side plate, the drive unit is connected to a rotation center of the second side plate, the center plate is fixed to a driven shaft portion connected to a rotation center of the driven-side end plate, a hole portion for the first side plate through which the driven shaft portion passes is formed in the first side plate, and a rotation center region of the second side plate is closed by a wall portion.
The first side plate is fixed to the drive-side wall body on the outer peripheral side, the second side plate is fixed to the first side plate, and the drive unit is connected to a substantial rotation center of the second side plate. As a result, a drive force is transmitted from the drive unit to the drive-side scroll member via the first side plate and the second side plate.
The drive force transmitted from both side plates via the synchronization drive mechanism is guided from the center plate to the driven-side scroll member by the center plate being fixed to the driven shaft portion connected to the rotation center of the driven-side end plate.
The driven shaft portion is disposed so as to pass through the hole portion for the first side plate formed in the first side plate. Since a drive force is transmitted from the center plate to the driven shaft portion via the synchronization drive mechanism, there is no need to form a hole portion for penetration by the driven shaft portion in the rotation center region of the second side plate. Accordingly, it is possible to adopt the second side plate that has a rotation center region closed by a wall portion, and thus lubricant leakage from the rotation center of the second side plate can be prevented.
The co-rotating scroll compressor according to an aspect of the present invention includes a drive-side scroll member driven to rotate around a rotational axis by a drive unit and having a spiral drive-side wall body disposed on a drive-side end plate, a driven-side scroll member in which a spiral driven-side wall body corresponding to the drive-side wall body is disposed on a driven-side end plate and the driven-side wall body meshes with the drive-side wall body to form a compression space, a synchronization drive mechanism transmitting a drive force of the drive unit to the driven-side scroll member such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity, a first side plate disposed on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member, a second side plate fixed at a predetermined gap in the rotational axis direction with respect to the first side plate, and a center plate disposed between the first side plate and the second side plate. The first side plate is fixed to one of the drive-side scroll member and the driven-side scroll member. The center plate is fixed to the other of the drive-side scroll member and the driven-side scroll member. The synchronization drive mechanism is provided with a round bar-shaped pin provided between the first and second side plates and the center plate and a ring guiding the pin by an inner peripheral surface of the ring abutting against an outer periphery of the pin.
A pin ring mechanism provided with the round bar-shaped pin and the ring is adopted as the synchronization drive mechanism. As a result, it is possible to realize the synchronization drive mechanism without adopting a crank pin mechanism, and thus it is possible to achieve cost reduction without a complex configuration caused by a large number of bearings being adopted as in the case of crank pin mechanisms.
In the co-rotating scroll compressor according to an aspect of the present invention, the ring is a rolling bearing provided on the center plate and both ends of the pin are press-fitted to the first side plate and the second side plate and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing.
The pin is press-fitted and fixed to both side plates, and thus the pin can be used as a positioning pin for both side plates.
Both ends of the pin are fixed to both side plates and the central portion of the pin abuts against the inner peripheral surface of the rolling bearing. Accordingly, inclination of the inner ring of the rolling bearing can be prevented, an oblique movement of a rolling member such as a ball can be prevented, and the life of the synchronization drive mechanism can be extended.
In the co-rotating scroll compressor according to an aspect of the present invention, the ring is a rolling bearing provided on the center plate and one end of the pin is press-fitted to one of the first side plate and the second side plate, the other end of the pin is fixed to the other of the first side plate and the second side plate via an elastic body, and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing.
One end of the pin is press-fitted and fixed to one of the side plates and the other end of the pin is fixed to the other of the side plates via the elastic body. As a result, both ends of the pin being incapable of being press-fitted to both side plates due to a component tolerance can be prevented, assembly can be facilitated, and cost reduction can be achieved.
In the co-rotating scroll compressor according to an aspect of the present invention, three or more synchronization drive mechanisms are provided to be spaced apart in a circumferential direction of the rotational axis, in two of the synchronization drive mechanisms, the ring is a rolling bearing provided on the center plate, both ends of the pin are press-fitted to the first side plate and the second side plate, and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing, and in the other synchronization drive mechanism, the ring is a rolling bearing provided on the center plate, one end of the pin is press-fitted to one of the first side plate and the second side plate, the other end of the pin is fixed to the other of the first side plate and the second side plate via an elastic body, and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing.
Two out of the three or more synchronization drive mechanisms have a function as a positioning pin as a configuration in which both ends of the pin are press-fitted and fixed to both side plates. As for the pin of the other synchronization drive mechanism, one end is press-fitted and fixed and the other end is fixed via the elastic body, which results in tolerance absorption. As a result, both side plates can be positioned by means of the synchronization drive mechanism and assemblability improvement can be achieved.
In the co-rotating scroll compressor according to an aspect of the present invention, the ring is a rolling bearing provided on each of the first side plate and the second side plate and a longitudinal central portion of the pin is press-fitted to the center plate and both ends of the pin abut against an inner peripheral surface of the rolling bearing.
The central portion of the pin is press-fitted to the center plate and both ends of the pin abut against the inner peripheral surfaces of the rolling bearings provided on both side plates. Accordingly, both ends of the pin are not restrained by both side plates, and thus it is possible to avoid a situation in which the pin cannot be fixed during assembly due to the component tolerance of both side plates. As a result, assemblability improvement can be achieved.
In the co-rotating scroll compressor according to an aspect of the present invention, the ring is a slide bearing instead of the rolling bearing.
It is possible to achieve cost reduction by replacing the rolling bearing with the slide bearing (such as a floating bush bearing).
The moment of inertia of a rotation system such as the rolling bearing can be reduced, and thus response enhancement can be achieved.
The co-rotating scroll compressor according to an aspect of the present invention includes a drive-side scroll member driven to rotate around a rotational axis by a drive unit and having a spiral drive-side wall body disposed on a drive-side end plate, a driven-side scroll member in which a spiral driven-side wall body corresponding to the drive-side wall body is disposed on a driven-side end plate and the driven-side wall body meshes with the drive-side wall body to form a compression space, a synchronization drive mechanism transmitting a drive force of the drive unit to the driven-side scroll member such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity, a first side plate disposed on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member, a second side plate fixed at a predetermined gap in the rotational axis direction with respect to the first side plate, and a center plate disposed between the first side plate and the second side plate. The first side plate is fixed to one of the drive-side scroll member and the driven-side scroll member. The center plate is fixed to the other of the drive-side scroll member and the driven-side scroll member. The synchronization drive mechanism is provided between the first and second side plates and the center plate and is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion, a first crank pin end portion rolling bearing provided between one end of the eccentric shaft portion and the first side plate, a second crank pin end portion rolling bearing provided between the other end of the eccentric shaft portion and the second side plate, and a cylindrical portion rolling bearing provided between the cylindrical portion and the center plate. An elastic body is provided in at least one of spaces between an outer ring of the first crank pin end portion rolling bearing and the first side plate, between an outer ring of the second crank pin end portion rolling bearing and the second side plate, and between an outer ring of the cylindrical portion rolling bearing and the center plate or in at least one of spaces between an inner ring of the first crank pin end portion rolling bearing and the one end of the eccentric shaft portion, between an inner ring of the second crank pin end portion rolling bearing and the other end of the eccentric shaft portion, and between an inner ring of the cylindrical portion rolling bearing and the cylindrical portion.
The elastic body is provided between the outer ring of the rolling bearing of the synchronization drive mechanism and the side plate or the center plate or between the inner ring of the rolling bearing of the synchronization drive mechanism and the crank pin. As a result, the tolerance of the crank pin, the side plates, and the center plate can be absorbed by the elastic body being deformed, internal force generation in the crank pin can be avoided, and the life of the synchronization drive mechanism can be extended.
In addition, the machining tolerance of the crank pin can be mitigated and machining and management costs can be reduced.
In addition, the outer ring is pressed to the inner ring side by the elastic body, and thus it is possible to prevent slipping between the outer ring and the hole in which the outer ring is fitted.
In the co-rotating scroll compressor according to an aspect of the present invention, the elastic body is provided between the outer ring of the cylindrical portion rolling bearing and the center plate, the outer ring of the first crank pin end portion rolling bearing is press-fitted to the first side plate, and the outer ring of the second crank pin end portion rolling bearing is press-fitted to the second side plate.
The outer ring of the first crank pin end portion rolling bearing and the outer ring of the second crank pin end portion rolling bearing are press-fitted, and thus a centrifugal force is held by both crank pin end portion rolling bearings. The two rolling bearings bear the centrifugal force in this manner, and thus the load to be borne can be mitigated as compared with a case where the single cylindrical portion rolling bearing bears the centrifugal force.
In addition, the crank pin is supported at both ends by the two crank pin end portion rolling bearings, and thus the posture of the crank pin can be stabilized.
In the co-rotating scroll compressor according to an aspect of the present invention, an insertion hole into which the eccentric shaft portion is inserted is formed in the cylindrical portion.
The eccentric shaft portion of the crank pin is inserted into the insertion hole formed in the cylindrical portion. As a result, the eccentric shaft portion and the cylindrical portion can be separate components and can be machined separately as for the crank pin. Accordingly, the axial centers at both ends of the eccentric shaft portion can be aligned as compared with a case where the eccentric shaft portion and the cylindrical portion are integrally machined.
The co-rotating scroll compressor according to an aspect of the present invention includes a drive-side scroll member driven to rotate around a rotational axis by a drive unit and having a spiral drive-side wall body disposed on a drive-side end plate, a driven-side scroll member in which a spiral driven-side wall body corresponding to the drive-side wall body is disposed on a driven-side end plate the driven-side wall body meshes with the drive-side wall body to form a compression space, a synchronization drive mechanism transmitting a drive force of the drive unit to the driven-side scroll member such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity, a first side plate disposed on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member, a second side plate fixed at a predetermined gap in the rotational axis direction with respect to the first side plate, and a center plate disposed between the first side plate and the second side plate. The first side plate is fixed to one of the drive-side scroll member and the driven-side scroll member. The center plate is fixed to the other of the drive-side scroll member and the driven-side scroll member. The synchronization drive mechanism is provided between the first and second side plates and the center plate and is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion. An insertion hole into which the eccentric shaft portion is inserted is formed in the cylindrical portion.
The eccentric shaft portion of the crank pin is inserted into the insertion hole formed in the cylindrical portion. As a result, the eccentric shaft portion and the cylindrical portion can be separate components and can be machined separately. Accordingly, the axial centers at both ends of the eccentric shaft portion can be aligned as compared with a case where the eccentric shaft portion and the cylindrical portion are integrally machined.
Accordingly, an internal force applied to the crank pin can be reduced and the life of the synchronization drive mechanism can be extended.

Advantageous Effects of Invention

Since the side plates and the center plate as members separate from the drive-side scroll member and the driven-side scroll member are provided with the synchronization drive mechanisms, heating attributable to the compression heat from the scroll members can be decreased and the life of the synchronization drive mechanisms can be extended.
The peripheral wall portion surrounding the outer peripheral side of the center plate is provided between the first side plate and the second side plate and the lubricant is held on the inner peripheral side of the peripheral wall portion, and thus the life of the synchronization drive mechanisms can be extended.
It is possible to simplify the configuration of the synchronization drive mechanism and achieve cost reduction by adopting the pin ring mechanism.
Tolerance absorption is performed by the elastic body being deformed, and thus internal force generation in the crank pin can be avoided and the life of the synchronization drive mechanisms can be extended.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a first embodiment of the present invention.

FIG. 2 is a perspective view illustrating a scroll member, both side plates, and a center plate of the co-rotating scroll compressor illustrated in FIG. 1.

FIG. 3 is a plan view illustrating the first drive-side scroll part illustrated in FIG. 1.

FIG. 4 is a plan view illustrating the second drive-side scroll part illustrated in FIG. 1.

FIG. 5 is a longitudinal cross-sectional view illustrating a second embodiment of the present invention and a part around a synchronization drive mechanism.

FIG. 6 is a longitudinal cross-sectional view illustrating Modification Example 1 of the second embodiment.

FIG. 7 is a longitudinal cross-sectional view illustrating Modification Example 2 of the second embodiment.

FIG. 8 is a longitudinal cross-sectional view illustrating a third embodiment of the present invention and a part around the synchronization drive mechanism.

FIG. 9 is a longitudinal cross-sectional view illustrating the co-rotating scroll compressor according to a fourth embodiment of the present invention.

FIG. 10 is a plan view illustrating the first drive-side wall body illustrated in FIG. 9.

FIG. 11 is a plan view illustrating the first driven-side wall body illustrated in FIG. 9.

FIG. 12 is a plan view illustrating the side plate and the center plate.

FIG. 13 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a fifth embodiment of the present invention.

FIG. 14 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a sixth embodiment of the present invention.

FIG. 15 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a seventh embodiment of the present invention.

FIG. 16 is a plan view illustrating the first drive-side wall body illustrated in FIG. 15.

FIG. 17 is a plan view illustrating the first driven-side wall body illustrated in FIG. 15.

FIG. 18 is a plan view illustrating the side plate and the center plate.

FIG. 19 is an enlarged longitudinal cross-sectional view illustrating a part around a pin ring mechanism.

FIG. 20 is a longitudinal cross-sectional view illustrating a modification example of the pin ring mechanism.

FIG. 21 is a longitudinal cross-sectional view illustrating a part around the pin ring mechanism of the co-rotating scroll compressor according to an eighth embodiment.

FIG. 22 is a longitudinal cross-sectional view illustrating a modification example of FIG. 21.

FIG. 23 is a longitudinal cross-sectional view illustrating a pin ring mechanism provided with a slide bearing as a modification example.

FIG. 24 is a longitudinal cross-sectional view illustrating the co-rotating scroll compressor according to a ninth embodiment of the present invention.

FIG. 25 is a plan view illustrating the first drive-side wall body illustrated in FIG. 24.

FIG. 26 is a plan view illustrating the first driven-side wall body illustrated in FIG. 24.

FIG. 27 is a plan view illustrating the side plate and the center plate.

FIG. 28 is a longitudinal cross-sectional view illustrating a part around an eccentric shaft portion of a crank pin.

FIG. 29 is a longitudinal cross-sectional view illustrating Modification Example 1 of the ninth embodiment.

FIG. 30 is a longitudinal cross-sectional view illustrating Modification Example 2 of the ninth embodiment.

FIG. 31 is a longitudinal cross-sectional view illustrating Modification Example 3 of the ninth embodiment.

FIG. 32A is a front view illustrating the crank pin of the co-rotating scroll compressor according to a tenth embodiment of the present invention.

FIG. 32B is a front view illustrating a crank pin as a reference example of FIG. 32A.

DESCRIPTION OF EMBODIMENTS

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.

First Embodiment

Hereinafter, a first embodiment of the present invention will be described with reference to the drawings including FIG. 1.
FIG. 1 illustrates a co-rotating scroll compressor 1. The co-rotating scroll compressor 1 can be used as a turbocharger compressing combustion air (a fluid) supplied to an internal combustion engine such as a vehicular engine, a compressor for supplying compressed air to an air electrode of a fuel cell, or a compressor for supplying compressed air used for a braking device of a vehicle such as a railway vehicle.
The co-rotating scroll compressor 1 is provided with a housing 3, a motor (drive unit) 5 accommodated on one end side of the housing 3, and a drive-side scroll member 70 and a driven-side scroll member 90 accommodated on the other end side of the housing 3.
The housing 3 has a substantially cylindrical shape and is provided with a motor accommodation portion 3 a accommodating the motor 5 and a scroll accommodation portion 3 b accommodating the scroll members 70 and 90.
A discharge port 3 d for discharging compressed air is formed in an end portion of the scroll accommodation portion 3 b. The housing 3 is provided with an air intake port (not illustrated in FIG. 1) suctioning air.
The motor 5 is driven by power being supplied from a power supply source (not illustrated). The rotation of the motor 5 is controlled by a command from a control unit (not illustrated). A stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3. A rotor 5 b of the motor 5 rotates around a drive-side rotational axis CL1. A drive shaft 6 extending on the drive-side rotational axis CL1 is connected to the rotor 5 b. The drive shaft 6 is connected to a shank 20 a of a center plate 20 driving a first drive-side scroll part 71 of the drive-side scroll member 70.
A drive-side bearing 11 rotatably supporting the drive shaft 6 is provided at the front end (left end in FIG. 1) of the drive shaft 6. A rear end bearing 17 rotatably supporting the drive shaft 6 between the housing 3 and the rear end bearing 17 is provided at the rear end (right end in FIG. 1) of the drive shaft 6, that is, in the end portion of the drive shaft 6 that is on the side opposite to the drive-side scroll member 70.
The drive-side scroll member 70 is provided with the first drive-side scroll part 71 on the motor 5 side and a second drive-side scroll part 72 on the discharge port 3 d side.
The first drive-side scroll part 71 is provided with a first drive-side end plate 71 a and a first drive-side wall body 71 b.
The first drive-side end plate 71 a extends in a direction orthogonal to the drive-side rotational axis CL1. The first drive-side end plate 71 a is fixed by means of a bolt 21 to a plurality of fixing portions 20 b provided on the outer periphery of the center plate 20. As illustrated in FIG. 2, three fixing portions 20 b of the center plate 20 are provided at substantially equal gaps in a circumferential direction. The fixing portion 20 b is not limited thereto in number.
The first drive-side end plate 71 a is substantially disk-shaped in plan view. As illustrated in FIG. 3, three spiral first drive-side wall bodies 71 b, that is, spiral first drive-side wall bodies 71 b in the form of three flights are provided on the first drive-side end plate 71 a. The first drive-side wall bodies 71 b in the form of three flights are disposed at equal gaps around the drive-side rotational axis CL1. Each of winding end portions 71 e of the first drive-side wall bodies 71 b is independent without being fixed to the other wall portion. In other words, a wall portion interconnecting and reinforcing the respective winding end portions 71 e is not provided. The first drive-side wall body 71 b may be one, two, or four or more in the number of flights.
As illustrated in FIG. 1, the second drive-side scroll part 72 is provided with a second drive-side end plate 72 a and a second drive-side wall body 72 b. The second drive-side wall body 72 b is in the form of three flights similarly to the first drive-side wall body 71 b (see FIG. 2) described above. Each of the winding end portions of the second drive-side wall bodies 72 b is independent without being fixed to the other wall portion. In other words, a wall portion interconnecting and reinforcing the respective winding end portions is not provided. The second drive-side wall body 72 b may be one, two, or four or more in the number of flights.
A second drive-side shaft portion 72 c extending in the drive-side rotational axis CL1 direction is connected to the second drive-side end plate 72 a. The second drive-side shaft portion 72 c is provided rotatably with respect to the housing 3 via a second drive-side bearing 14, which is a ball bearing. The second drive-side end plate 72 a is provided with a discharge port 72 d, which is along the drive-side rotational axis CL1.
Two seal members 26 are provided between the second drive-side shaft portion 72 c and the housing 3 and on the leading edge side (left side in FIG. 1) of the second drive-side shaft portion 72 c beyond the second drive-side bearing 14. The two seal members 26 and the second drive-side bearing 14 are disposed at predetermined gaps in the drive-side rotational axis CL1 direction. Enclosed between the two seal members 26 is a lubricant that is grease such as a semi-solid lubricant. The seal member 26 may be one in number. In this case, the lubricant is enclosed between the seal member 26 and the second drive-side bearing 14.
The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed in a state where the leading edges (free ends) of the wall bodies 71 b and 72 b face each other. The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed by a bolt 31, which is fastened to flange portions 73 provided at a plurality of places in the circumferential direction so as to protrude to a radial outer side.
In the driven-side scroll member 90, a driven-side end plate 90 a is positioned substantially at the center in an axial direction (the horizontal direction in the drawing). A through-hole 90 h is formed at the center of the driven-side end plate 90 a and compressed air flows to the discharge port 72 d.
A first driven-side wall body 91 b and a second driven-side wall body 92 b are provided on both sides of the driven-side end plate 90 a, respectively. The first driven-side wall body 91 b installed on the motor 5 side from the driven-side end plate 90 a meshes with the first drive-side wall body 71 b of the first drive-side scroll part 71 and the second driven-side wall body 92 b installed on the discharge port 3 d side from the driven-side end plate 90 a meshes with the second drive-side wall body 72 b of the second drive-side scroll part 72.
Three first driven-side wall bodies 91 b, that is, first driven-side wall bodies 91 b in the form of three flights are provided as illustrated in FIG. 4. The driven-side wall bodies 91 b in the form of three flights are disposed at equal gaps around a driven-side rotational axis CL2. The second driven-side wall body 92 b is similar in configuration. Each of the driven- side wall bodies 91 b and 92 b may be one, two, or four or more in the number of flights.
A support member 33 is provided on the discharge port 3 d side (left side in FIG. 1) of the driven-side scroll member 90. The support member 33 is fixed by a bolt 25 to the leading edge (free end) of the second driven-side wall body 92 b.
A shank 35 a for the support member is provided on the central axis side of the support member 33 and the shank 35 a for the support member is fixed to the housing 3 via a bearing 38 for a second support member, which is an angular ball bearing. As a result, the driven-side scroll member rotates around the second central axis CL2 via the support member 33.
A first side plate 27 is provided on the motor 5 side (right side in FIG. 1) of the driven-side scroll member 90. The first side plate 27 is fixed by a bolt 28 to the leading edge (free end) of the first driven-side wall body 91 b.
A second side plate 30 is provided at a predetermined gap on the motor 5 side of the first side plate 27. The second side plate 30 is fixed by the bolt 31 to the first side plate 27. A shank 30 a for the second side plate is provided on the central axis side of the second side plate 30 and the shank 30 a for the second side plate is fixed to the housing 3 via a bearing 32 for the second side plate, which is an angular ball bearing. As a result, the driven-side scroll member 90 rotates around the second central axis CL2 via the second side plate 30 and the first side plate 27.
The center plate 20 is disposed between the first side plate 27 and the second side plate 30. As illustrated in FIG. 2, the center plate 20 is directly fixed to the drive-side scroll member 70 and the first side plate 27 is directly fixed to the driven-side scroll member 90.
A crank pin 15 is provided between the first and second side plates 27 and 30 and the center plate 20. The crank pin 15 has a cylindrical portion 15 a at the center and an eccentric shaft portion 15 b, which has an eccentric axis (see reference sign CL3 in FIG. 5) eccentric to the central axis of the cylindrical portion 15 a.
Provided on the outer periphery of the cylindrical portion 15 a is a bearing 16 for the cylindrical portion, which is an angular ball bearing. As a result, the cylindrical portion 15 a is rotatable with respect to the center plate 20.
A bearing 18 a for a first eccentric shaft portion (crank pin end portion rolling bearing) and a bearing 18 b for a second eccentric shaft portion (crank pin end portion rolling bearing), which are angular ball bearings, are provided at both ends of the eccentric shaft portion 15 b, respectively. As a result, the eccentric shaft portion 15 b is rotatable with respect to the first side plate 27 and the second side plate 30.
The crank pin 15 and the respective bearings 16, 18 a, and 18 b are used as synchronization drive mechanisms transmitting the drive force of the motor 5 to the driven-side scroll member 90 such that both scroll members 70 and 90 perform revolving and orbiting motions in synchronization.
It is preferable that a plurality of the synchronization drive mechanisms provided with the crank pin 15 are provided. For example, three synchronization drive mechanisms are provided at equal angular gaps around the drive-side rotational axis CL3.
The co-rotating scroll compressor 1 configured as described above operates as follows.
The drive shaft 6 is rotated around the drive-side rotational axis CL1 by the motor 5, and then the center plate 20 also rotates via the shank 20 a connected to the drive shaft 6. By the center plate 20 rotating, the drive-side scroll member 70 connected via the fixing portion 20 b rotates around the drive-side rotational axis CL1. The drive force transmitted to the center plate 20 is transmitted from the first side plate 27 and the second side plate 30 to the driven-side scroll member 90 via the crank pin 15 as a synchronization drive mechanism and the driven-side scroll member 90 rotates around the driven-side rotational axis CL2. At this time, the crank pin 15 rotates with respect to the center plate 20 and both side plates via the respective bearings 16, 18 a, and 18 b, and thus both scroll members 70 and 90 relatively perform the revolving and orbiting motions.
By both scroll members 70 and 90 performing the revolving and orbiting motions, the air suctioned from the intake port of the housing 3 is suctioned from the outer peripheral sides of both scroll members 70 and 90 and taken into the compression chamber formed by both scroll members 70 and 90. Then, the compression chamber formed by the first drive-side wall body 71 b and the first driven-side wall body 91 b and the compression chamber formed by the second drive-side wall body 72 b and the second driven-side wall body 92 b are separately compressed. The air is compressed as the volume of each compression chamber decreases with a movement to the center side. The air compressed by the first drive-side wall body 71 b and the first driven-side wall body 91 b passes through the through-hole 90 h formed in the driven-side end plate 90 a and merges with the air compressed by the second drive-side wall body 72 b and the second driven-side wall body 92 b, and the merged air is discharged from the discharge port 3 d of the housing 3 to the outside through the discharge port 72 d.
The present embodiment has the following action and effect.
The first side plate 27 and the second side plate 30 are provided on the rotational axis direction CL1 side and the rotational axis direction CL2 side with respect to the drive-side scroll member 70 and the driven-side scroll member 90 and the center plate 20 is provided between the side plates 27 and 30. The crank pin 15 and the respective bearings 16, 18 a, and 18 b are provided as the synchronization drive mechanisms between both side plates 27 and 30 and the center plate 20. Since the side plates 27 and 30 and the center plate 20 as members separate from both scroll members 70 and 90 are provided with the synchronization drive mechanisms as described above, heating attributable to the compression heat from the scroll members 70 and 90 can be decreased as compared with a case where a synchronization drive mechanism is provided with respect to end plates of the scroll members 70 and 90 and the life of the synchronization drive mechanisms can be extended.
A load is applied to the crank pin 15 from the center plate 20 and the side plates 27 and 30 on both sides thereof, and thus the moment around the cylindrical portion 15 a of the crank pin 15 can be canceled and the life of the synchronization drive mechanisms can be extended.
The synchronization drive mechanisms are disposed by both side plates 27 and 30 and the center plate 20 being provided on the rotational axis CL1 direction side and the rotational axis CL2 direction side, and thus diameter reduction can be achieved as compared with a case where a synchronization drive mechanism is provided on radial direction sides of the scroll members 70 and 90.
Although the crank pin 15 is used as a synchronization drive mechanism in the present embodiment, the present invention is not limited thereto. For example, a pin ring mechanism that a pin member and a ring member constitute may be used.

Second Embodiment

Next, a second embodiment of the present invention will be described. The present embodiment relates to a synchronization drive mechanism provided with the crank pin 15 described in the first embodiment. Accordingly, the overall configuration of the co-rotating scroll compressor 1 is similar to that of the first embodiment and will not be described below.
As illustrated in FIG. 5, in end portions 15 c on both sides of the eccentric shaft portion 15 b of the crank pin 15, small-diameter portions 15 d smaller in diameter than a central portion 15 e are provided at the positions where the inner rings of the bearings 18 a and 18 b for the eccentric shaft portions are attached. A step section 15 j between the central portion 15 e and the small-diameter portion 15 d is provided with an O-ring (urging member) 19.
The O-ring 19 urges the inner rings of the bearings 18 a and 18 b for the eccentric shaft portions in the eccentric axis CL3 direction toward the leading edge of the crank pin 15.
In FIG. 5, reference sign 41 denotes a seal plate for sealing a lubricant and reference sign 42 denotes a stopper ring for fixing the seal plate 41.
The present embodiment has the following action and effect.
The O-ring 19 is provided between the inner rings of the bearings 18 a and 18 b for the eccentric shaft portions and the eccentric shaft portion 15 b of the crank pin 15 and the O-ring 19 urges the inner rings in the eccentric axis CL3 direction toward the leading edge of the eccentric shaft portion 15 b. The O-ring 19 urges the inner rings of the bearings 18 a and 18 b for the eccentric shaft portions toward the leading edge, and thus an outer ring is pressed against the side plates 27 and 30 via the balls (rolling bodies) of the bearings 18 a and 18 b for the eccentric shaft portions. As a result, the bearings 18 a and 18 b for the eccentric shaft portions are put into a state where a preload is applied between the eccentric shaft portion 15 b of the crank pin 15 and the side plates 27 and 30, it is possible to prevent slipping between the ball and the inner ring and slipping between the inner ring and the eccentric shaft portion 15 b, and the life of the synchronization drive mechanism can be extended.

Modification Example 1

The configuration illustrated in FIG. 6 may be adopted, instead of or along with the present embodiment, as means for applying a preload to the bearings 18 a and 18 b for the eccentric shaft portions.
FIG. 6 illustrates a state where the second side plate 30 is yet to be fixed to the first side plate 27 by the bolt 31. In this state, a gap t is formed between the first side plate 27 and the leading edge of a fixing portion 30 b of the second side plate 30. In this manner, the gap determined by both side plates 27 and 30 being fastened by means of the bolt 31 is kept smaller than the gap between both side plates 27 and 30 determined by the crank pin 15 and the respective bearings 16, 18 a, and 18 b. As a result, the gap between the side plates 27 and 30 is narrowed when the second side plate 30 is fastened to the first side plate 27 by means of the bolt 31 and a preload can be applied in the eccentric axis CL3 direction to the bearings 18 a and 18 b for the eccentric shaft portions.

Modification Example 2

The configuration illustrated in FIG. 7 may be adopted, instead of or along with the present embodiment, as means for preventing the inner rings of the bearings 18 a and 18 b for the eccentric shaft portions from slipping.
As illustrated in FIG. 7, an O-ring (elastic body) 22 is provided between the inner peripheral surface of the inner ring of the bearing 18 a for the first eccentric shaft portion and the outer peripheral surface of the eccentric shaft portion 15 b. The O-ring 22 urges the inner ring of the bearing 18 a for the first eccentric shaft portion to the radial outer side about the eccentric axis CL3 by means of the reaction force resulting from deformation of the O-ring 22. As a result, slipping between the eccentric shaft portion 15 b and the inner ring can be prevented.
The bearing 18 b for the second eccentric shaft portion may be provided with the O-ring 22.

Third Embodiment

Next, a third embodiment of the present invention will be described. The present embodiment is different from the first embodiment in terms of the fixing portion 20 b fixing the center plate 20 to the drive-side scroll member 70. The third embodiment is similar to the first embodiment regarding the other points, and thus the points will not be described below.
As illustrated in FIG. 8, a fixing portion 20 b′ of the center plate 20 is positioned on the drive-side rotational axis CL1 side with respect to a fixing portion 27 a of the first side plate 27 and the fixing portion 30 b of the second side plate 30. The fixing portion 20 b′ of the center plate 20 has a structure in which a resinous shaft portion 40 made of resin is interposed. The other part of the center plate 20 is metallic and made of aluminum alloy or iron.
The fixing portion 27 a of the first side plate 27 and the fixing portion 30 b of the second side plate 30 have a metallic structure without resin portion interposition.
The present embodiment has the following action and effect.
The structure in which the resinous shaft portion 40 is interposed is because the temperature of the fixing portion 20 b′ of the center plate 20, which is positioned radially inward of the centers of the scroll members 70 and 90, tends to rise due to compression heat. As a result, it is possible to achieve life extension by suppressing a rise in the temperature of the synchronization drive mechanism provided with the crank pin 15.
The metallic structure without resin portion interposition is because a rise in temperature attributable to compression heat has little effect on the fixing portion 27 a of the first side plate 27 and the fixing portion 30 b of the second side plate 30, which are positioned radially outward of the centers of the scroll members 70 and 90. As a result, the fixing portions 27 a and 30 b can be accurately assembled by means of metal, and thus the synchronization drive mechanism can be accurately positioned, phase shift reduction can be achieved between the drive-side scroll member 70 and the driven-side scroll member 90, and compression performance improvement can be achieved.

Fourth Embodiment

Hereinafter, a fourth embodiment of the present invention will be described with reference to the drawings including FIG. 9.
FIG. 9 illustrates the co-rotating scroll compressor 1. The co-rotating scroll compressor 1 can be used as a turbocharger compressing combustion air (a fluid) supplied to an internal combustion engine such as a vehicular engine, a compressor for supplying compressed air to an electrode of a fuel cell, or a compressor for supplying compressed air used for a braking device of a vehicle such as a railway vehicle.
The co-rotating scroll compressor 1 is provided with the housing 3, the motor (drive unit) 5 accommodated on one end side of the housing 3, and the drive-side scroll member 70 and the driven-side scroll member 90 accommodated on the other end side of the housing 3.
The housing 3 has a substantially cylindrical shape and is provided with the motor accommodation portion 3 a accommodating the motor 5 and the scroll accommodation portion 3 b accommodating the scroll members 70 and 90.
The discharge port 3 d for discharging compressed air is formed in an end portion of the scroll accommodation portion 3 b. The housing 3 is provided with an air intake port (not illustrated in FIG. 9) suctioning air.
The motor 5 is driven by power being supplied from a power supply source (not illustrated). The rotation of the motor 5 is controlled by a command from a control unit (not illustrated). The stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3. The rotor 5 b of the motor 5 rotates around the drive-side rotational axis CL1. The drive shaft 6 extending on the drive-side rotational axis CL1 is connected to the rotor 5 b. The drive shaft 6 is connected to a drive shaft portion 71 d fixed to the first drive-side scroll part 71 of the drive-side scroll member 70.
The drive-side bearing 11 rotatably supporting the drive shaft 6 is provided at the front end (left end in FIG. 9) of the drive shaft 6. The rear end bearing 17 rotatably supporting the drive shaft 6 between the housing 3 and the rear end bearing 17 is provided at the rear end (right end in FIG. 9) of the drive shaft 6, that is, in the end portion of the drive shaft 6 that is on the side opposite to the drive-side scroll member 70.
The drive-side scroll member 70 is provided with the first drive-side scroll part 71 on the motor 5 side and the second drive-side scroll part 72 on the discharge port 3 d side.
The first drive-side scroll part 71 is provided with the first drive-side end plate 71 a and the first drive-side wall body 71 b.
The first drive-side end plate 71 a extends in a direction orthogonal to the drive-side rotational axis CL1. The drive shaft portion 71 d extending on and along the drive-side rotational axis CL1 is fixed to the rotation center of the first drive-side end plate 71 a.
The center plate 20 is fixed to the drive shaft portion 71 d. The center plate 20 extends in parallel with the first drive-side end plate 71 a.
The first drive-side end plate 71 a is substantially disk-shaped in plan view. As illustrated in FIG. 10, the three spiral first drive-side wall bodies 71 b, that is, the spiral first drive-side wall bodies 71 b in the form of three flights are provided on the first drive-side end plate 71 a. The first drive-side wall bodies 71 b in the form of three flights are disposed at equal gaps around the drive-side rotational axis CL1. The first drive-side wall body 71 b may be one, two, or four or more in the number of flights.
As illustrated in FIG. 9, the second drive-side scroll part 72 is provided with the second drive-side end plate 72 a and the second drive-side wall body 72 b. The second drive-side wall body 72 b is in the form of three flights similarly to the first drive-side wall body 71 b (see FIG. 10) described above. The second drive-side wall body 72 b may be one, two, or four or more in the number of flights.
The second drive-side shaft portion 72 c extending in the drive-side rotational axis CL1 direction is connected to the second drive-side end plate 72 a. The second drive-side shaft portion 72 c is provided rotatably with respect to the housing 3 via the second drive-side bearing 14, which is a ball bearing. The second drive-side end plate 72 a is provided with the discharge port 72 d, which is along the drive-side rotational axis CL1.
The two seal members 26 are provided between the second drive-side shaft portion 72 c and the housing 3 and on the leading edge side (left side in FIG. 9) of the second drive-side shaft portion 72 c beyond the second drive-side bearing 14. The two seal members 26 and the second drive-side bearing 14 are disposed at predetermined gaps in the drive-side rotational axis CL1 direction. Enclosed between the two seal members 26 is a lubricant that is grease such as a semi-solid lubricant. The seal member 26 may be one in number. In this case, the lubricant is enclosed between the seal member 26 and the second drive-side bearing 14.
The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed in a state where the leading edges (free ends) of the wall bodies 71 b and 72 b face each other. The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed by the bolt 31, which is fastened to the flange portions 73 provided at a plurality of places in the circumferential direction so as to protrude to the radial outer side.
In the driven-side scroll member 90, the driven-side end plate 90 a is positioned substantially at the center in the axial direction (horizontal direction in the drawing). The through-hole 90 h is formed at the center of the driven-side end plate 90 a and compressed air flows to the discharge port 72 d.
The first driven-side wall body 91 b and the second driven-side wall body 92 b are provided on both sides of the driven-side end plate 90 a, respectively. The first driven-side wall body 91 b installed on the motor 5 side from the driven-side end plate 90 a meshes with the first drive-side wall body 71 b of the first drive-side scroll part 71 and the second driven-side wall body 92 b installed on the discharge port 3 d side from the driven-side end plate 90 a meshes with the second drive-side wall body 72 b of the second drive-side scroll part 72.
The three first driven-side wall bodies 91 b, that is, the first driven-side wall bodies 91 b in the form of three flights are provided as illustrated in FIG. 11. The driven-side wall bodies 91 b in the form of three flights are disposed at equal gaps around the driven-side rotational axis CL2. The second driven-side wall body 92 b is similar in configuration. Each of the driven- side wall bodies 91 b and 92 b may be one, two, or four or more in the number of flights.
The support member 33 is provided on the discharge port 3 d side (left side in FIG. 9) of the driven-side scroll member 90. The support member 33 is fixed by the bolt 25 to the leading edge (free end) of the second driven-side wall body 92 b.
The shank 35 a for the support member is provided on the central axis side of the support member 33 and the shank 35 a for the support member is fixed to the housing 3 via the bearing 38 for the second support member, which is an angular ball bearing. As a result, the driven-side scroll member 90 rotates around the driven-side rotational axis CL2 via the support member 33.
The first side plate 27 is provided on the motor 5 side (right side in FIG. 9) of the driven-side scroll member 90. The first side plate 27 is fixed by the bolt 28 to the leading edge (free end) of the first driven-side wall body 91 b. Formed at the rotation center of the first side plate is a hole portion 27 h for the first side plate for penetration by the drive shaft portion 71 d.
The second side plate 30 is provided at a predetermined gap on the motor 5 side of the first side plate 27. The second side plate 30 is fixed by a bolt 34 to the first side plate 27. Formed at the rotation center of the second side plate 30 is a hole portion 30 h for the second side plate for penetration by the drive shaft portion 71 d.
The shank 30 a for the second side plate is provided on the central axis side of the second side plate 30 and the shank 30 a for the second side plate is fixed to the housing 3 via the bearing 32 for the second side plate, which is an angular ball bearing. As a result, the driven-side scroll member 90 rotates around the driven-side rotational axis CL2 via the second side plate 30 and the first side plate 27.
A first protruding wall portion 27 b protruding toward the second side plate 30 is provided on the outer peripheral side end surface of the first side plate 27. A second protruding wall portion 30 c protruding toward the first side plate 27 is provided on the outer peripheral side end surface of the second side plate 30. The protruding wall portions 27 b and 30 c constitute a peripheral wall portion by being attached to each other and fixed in a liquid-tight state. As a result, the center plate 20 disposed between the first side plate 27 and the second side plate 30 is accommodated in a space S surrounded by both protruding wall portions 27 b and 30 c as illustrated in FIG. 12.
As illustrated in FIG. 9, the crank pin 15 is provided between the first and second side plates 27 and 30 and the center plate 20. The crank pin 15 has the cylindrical portion 15 a at the center and the eccentric shaft portion 15 b, which has an eccentric axis eccentric to the central axis of the cylindrical portion 15 a.
Provided on the outer periphery of the cylindrical portion 15 a is the bearing 16 for the cylindrical portion, which is a ball bearing. As a result, the cylindrical portion 15 a is rotatable with respect to the center plate 20. A lubricant such as grease is enclosed in the bearing 16 for the cylindrical portion.
The bearing 18 a for the first eccentric shaft portion (crank pin end portion rolling bearing 18 a) and the bearing 18 b for the second eccentric shaft portion (crank pin end portion rolling bearing 18 b), which are ball bearings, are provided at both ends of the eccentric shaft portion 15 b, respectively. As a result, the eccentric shaft portion 15 b is rotatable with respect to the first side plate 27 and the second side plate 30. A lubricant such as grease is enclosed in each of the bearings 18 a and 18 b for the eccentric shaft portions.
The crank pin 15 and the respective bearings 16, 18 a, and 18 b are used as synchronization drive mechanisms transmitting a drive force from the drive shaft portion 71 d to the driven-side scroll member 90 such that both scroll members 70 and 90 perform revolving and orbiting motions in synchronization.
It is preferable that a plurality of the synchronization drive mechanisms provided with the crank pin 15 are provided. For example, three synchronization drive mechanisms are provided at equal angular gaps around the drive-side rotational axis CL3 (see FIG. 12).
The co-rotating scroll compressor 1 configured as described above operates as follows.
The drive shaft 6 is rotated around the drive-side rotational axis CL1 by the motor 5, and then the center plate 20 as well as the drive-side scroll member 70 rotates around the drive-side axis CL1 via the drive shaft portion 71 d connected to the drive shaft 6. By the center plate 20 rotating, the drive force transmitted to the center plate is transmitted from the first side plate 27 and the second side plate 30 to the driven-side scroll member 90 via the crank pin 15 as a synchronization drive mechanism and the driven-side scroll member 90 rotates around the driven-side rotational axis CL2. At this time, the crank pin 15 rotates with respect to the center plate 20 and both side plates via the respective bearings 16, 18 a, and 18 b, and thus both scroll members 70 and 90 relatively perform the revolving and orbiting motions.
By both scroll members 70 and 90 performing the revolving and orbiting motions, the air suctioned from the intake port of the housing 3 is suctioned from the outer peripheral sides of both scroll members 70 and 90 and taken into the compression chamber formed by both scroll members 70 and 90. Then, the compression chamber formed by the first drive-side wall body 71 b and the first driven-side wall body 91 b and the compression chamber formed by the second drive-side wall body 72 b and the second driven-side wall body 92 b are separately compressed. The air is compressed as the volume of each compression chamber decreases with a movement to the center side. The air compressed by the first drive-side wall body 71 b and the first driven-side wall body 91 b passes through the through-hole 90 h formed in the driven-side end plate 90 a and merges with the air compressed by the second drive-side wall body 72 b and the second driven-side wall body 92 b, and the merged air is discharged from the discharge port 3 d of the housing 3 to the outside through the discharge port 72 d.
The present embodiment has the following action and effect.
The first side plate 27 and the second side plate 30 are provided on the rotational axis CL1 direction side and the rotational axis CL2 direction side with respect to the drive-side scroll member 70 and the driven-side scroll member 90 and the center plate 20 is provided between the side plates 27 and 30. The crank pin 15 and the respective bearings 16, 18 a, and 18 b are provided as the synchronization drive mechanisms between both side plates 27 and 30 and the center plate 20. Further, the first protruding wall portion 27 b and the second protruding wall portion 30 c are provided between the first side plate 27 and the second side plate 30 as the peripheral wall portion surrounding the outer peripheral side of the center plate 20. As a result, even when the lubricant supplied to the synchronization drive mechanism (specifically, each of the bearings 16, 18 a, and 18 b) is moved to the outer peripheral side by a centrifugal force, the lubricant can be held on the inner peripheral side of the liquid-tight peripheral wall portion, and thus an insufficient lubrication of the synchronization drive mechanism can be avoided and life extension can be achieved.
In addition, it is possible to prevent the compressed air from being contaminated by preventing lubricant leakage.
Although the peripheral wall portion is constituted by means of the first protruding wall portion 27 b and the second protruding wall portion 30 c in the present embodiment, the present invention is not limited thereto. The peripheral wall portion may be provided so as to surround the outer periphery of the center plate 20. For example, the first protruding wall portion 27 b may constitute the peripheral wall portion alone or the second protruding wall portion 30 c may constitute the peripheral wall portion alone. In addition, the peripheral wall portion may be configured by means of a member other than the side plates 27 and 30.
Although the crank pin 15 is used as a synchronization drive mechanism in the present embodiment, the present invention is not limited thereto and the synchronization drive mechanism may be any synchronization drive mechanism requiring lubricant supply. For example, a pin ring mechanism that a pin member and a ring member constitute may be used.

Fifth Embodiment

Next, a fifth embodiment of the present invention will be described. The present embodiment differs from the fourth embodiment in that a seal member is provided with respect to the side plates 27 and 30. Accordingly, the overall configuration of the co-rotating scroll compressor 1 is similar to that of the fourth embodiment and will not be described below.
As illustrated in FIG. 13, a first seal member 43 is provided between the first side plate 27 and the drive shaft portion 71 d. A boots seal or a labyrinth seal can be adopted as the first seal member 43.
A second seal member 44 is provided between end surfaces of the second side plate 30 and the center plate 20. An annular and resinous tip seal can be adopted as the second seal member 44. The second seal member 44 is accommodated in a circumferential groove formed in the end surface of the second side plate 30. The second seal member 44 may be installed on the center plate 20 side by means of circumferential groove formation in the center plate 20.
The present embodiment has the following action and effect.
Sealing is performed between the first side plate 27 and the drive shaft portion 71 d by the first seal member 43 being provided. As a result, it is possible to prevent lubricant leakage from the space between the first side plate 27 and the drive shaft portion 71 d. The first seal member 43 may be provided between the second side plate 30 and the drive shaft portion 71 d.
The second seal member 44 is provided between the second side plate 30 and the center plate 20. As a result, it is possible to prevent lubricant leakage from the space between the second side plate 30 and the drive shaft portion 71 d. The second seal member 44 may be provided between the first side plate 27 and the center plate 20.

Sixth Embodiment

Next, a sixth embodiment of the present invention will be described. The present embodiment differs from the fourth embodiment in that the side plates 27 and 30 are the drive side and the center plate 20 is the driven side. The sixth embodiment is similar to the fourth embodiment regarding the other points, and thus the points will not be described below.
As illustrated in FIG. 14, the drive shaft 6 (see FIG. 9) of the motor 5 is connected to a drive shaft portion 30 d protruding to the motor 5 side from the rotation center of the second side plate 30. Accordingly, the drive force from the motor 5 is transmitted from the second side plate 30 to a drive-side scroll member 50 via the first side plate 27. In other words, the driven-side scroll member 90 of the fourth embodiment is the drive side.
A drive force is transmitted from both side plates 27 and 30 to the center plate 20 via the synchronization drive mechanism provided with the crank pin 15. A driven shaft portion 61 d is fixed to the center plate 20. The driven shaft portion 61 d is provided at the rotation center of a first driven-side end plate 61 a of a driven-side scroll member 60. Accordingly, the drive-side scroll member 70 of the fourth embodiment is the driven side.
As in the fourth embodiment, the first protruding wall portion 27 b of the first side plate 27 and the second protruding wall portion 30 c of the second side plate 30 constitute a peripheral wall portion. Accordingly, the configuration, action, and effect thereof will not be described below.
Unlike in the fourth embodiment, the rotation center region of the second side plate 30 is not provided with a hole portion (the hole portion 30 h for the second side plate: see FIG. 9). The rotation center region of the second side plate 30 is closed by a wall portion.
The present embodiment has the following action and effect.
The drive shaft portion 30 d is provided with respect to the rotation center of the second side plate 30. As a result, a drive force is transmitted from the motor 5 to the drive-side scroll member 50 via the first side plate 27 and the second side plate 30.
The drive force transmitted from both side plates 27 and 30 via the synchronization drive mechanism is guided from the center plate 20 to the driven-side scroll member 60 by the center plate 20 being fixed to the driven shaft portion 61 d connected to the rotation center of the first driven-side end plate 61 a of the driven-side scroll member 60. The driven shaft portion 61 d is disposed so as to pass through the hole portion 27 h for the first side plate formed in the first side plate 27. Since a drive force is transmitted from the center plate 20 to the driven shaft portion 61 d via the synchronization drive mechanism, there is no need to form a hole portion for penetration by the driven shaft portion 61 d in the rotation center region of the second side plate 30. Accordingly, it is possible to adopt the second side plate 30 that has a rotation center region closed by a wall portion, and thus lubricant leakage from the rotation center of the second side plate 30 can be prevented.
In addition, there is no need to provide a bearing rotatably supporting the driven shaft portion 61 d. Accordingly, the drive-side bearing 11 (see FIG. 9) of the fourth embodiment can be omitted and the number of components can be reduced.

Seventh Embodiment

Hereinafter, a seventh embodiment of the present invention will be described with reference to the drawings including FIG. 15.
FIG. 15 illustrates the co-rotating scroll compressor 1. The co-rotating scroll compressor 1 can be used as a turbocharger compressing combustion air (a fluid) supplied to an internal combustion engine such as a vehicular engine, a compressor for supplying compressed air to an air electrode of a fuel cell, or a compressor for supplying compressed air used for a braking device of a vehicle such as a railway vehicle.
The co-rotating scroll compressor 1 is provided with the housing 3, the motor (drive unit) 5 accommodated on one end side of the housing 3, and the drive-side scroll member 70 and the driven-side scroll member 90 accommodated on the other end side of the housing 3.
The housing 3 has a substantially cylindrical shape and is provided with the motor accommodation portion 3 a accommodating the motor 5 and the scroll accommodation portion 3 b accommodating the scroll members 70 and 90.
The discharge port 3 d for discharging compressed air is formed in an end portion of the scroll accommodation portion 3 b. The housing 3 is provided with an air intake port (not illustrated in FIG. 15) suctioning air.
The motor 5 is driven by power being supplied from a power supply source (not illustrated). The rotation of the motor 5 is controlled by a command from a control unit (not illustrated). The stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3. The rotor 5 b of the motor 5 rotates around the drive-side rotational axis CL1. The drive shaft 6 extending on the drive-side rotational axis CL1 is connected to the rotor 5 b. The drive shaft 6 is connected to the drive shaft portion 71 d fixed to the first drive-side scroll part 71 of the drive-side scroll member 70.
The drive-side bearing 11 rotatably supporting the drive shaft 6 is provided at the front end (left end in FIG. 15) of the drive shaft 6. A rear end bearing 24 rotatably supporting the drive shaft 6 between the housing 3 and the rear end bearing 24 is provided at the rear end (right end in FIG. 15) of the drive shaft 6, that is, in the end portion of the drive shaft 6 that is on the side opposite to the drive-side scroll member 70.
The drive-side scroll member 70 is provided with the first drive-side scroll part 71 on the motor 5 side and the second drive-side scroll part 72 on the discharge port 3 d side.
The first drive-side scroll part 71 is provided with the first drive-side end plate 71 a and the first drive-side wall body 71 b.
The first drive-side end plate 71 a extends in a direction orthogonal to the drive-side rotational axis CL1. The drive shaft portion 71 d extending on and along the drive-side rotational axis CL1 is fixed to the rotation center of the first drive-side end plate 71 a.
The center plate 20 is fixed to the drive shaft portion 71 d. The center plate 20 extends in parallel with the first drive-side end plate 71 a.
The first drive-side end plate 71 a is substantially disk-shaped in plan view. As illustrated in FIG. 16, the three spiral first drive-side wall bodies 71 b, that is, the spiral first drive-side wall bodies 71 b in the form of three flights are provided on the first drive-side end plate 71 a. The first drive-side wall bodies 71 b in the form of three flights are disposed at equal gaps around the drive-side rotational axis CL1. The first drive-side wall body 71 b may be one, two, or four or more in the number of flights.
As illustrated in FIG. 15, the second drive-side scroll part 72 is provided with the second drive-side end plate 72 a and the second drive-side wall body 72 b. The second drive-side wall body 72 b is in the form of three flights similarly to the first drive-side wall body 71 b (see FIG. 16) described above. The second drive-side wall body 72 b may be one, two, or four or more in the number of flights.
The second drive-side shaft portion 72 c extending in the drive-side rotational axis CL1 direction is connected to the second drive-side end plate 72 a. The second drive-side shaft portion 72 c is provided rotatably with respect to the housing 3 via the second drive-side bearing 14, which is a ball bearing. The second drive-side end plate 72 a is provided with the discharge port 72 d, which is along the drive-side rotational axis CL1.
The two seal members 26 for a second drive shaft portion are provided between the second drive-side shaft portion 72 c and the housing 3 and on the leading edge side (left side in FIG. 15) of the second drive-side shaft portion 72 c beyond the second drive-side bearing 14. The two seal members 26 for the second drive shaft portion and the second drive-side bearing 14 are disposed at predetermined gaps in the drive-side rotational axis CL1 direction. Enclosed between the two seal members 26 for the second drive shaft portion is a lubricant that is grease such as a semi-solid lubricant. The seal member 26 for the second drive shaft portion may be one in number. In this case, the lubricant is enclosed between the seal member 26 for the second drive shaft portion and the second drive-side bearing 14.
The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed in a state where the leading edges (free ends) of the wall bodies 71 b and 72 b face each other. The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed by the bolt 31, which is fastened to the flange portions 73 provided at a plurality of places in the circumferential direction so as to protrude to the radial outer side.
In the driven-side scroll member 90, the driven-side end plate 90 a is positioned substantially at the center in the axial direction (horizontal direction in the drawing). The through-hole 90 h is formed at the center of the driven-side end plate 90 a and compressed air flows to the discharge port 72 d.
The first driven-side wall body 91 b and the second driven-side wall body 92 b are provided on both sides of the driven-side end plate 90 a, respectively. The first driven-side wall body 91 b installed on the motor 5 side from the driven-side end plate 90 a meshes with the first drive-side wall body 71 b of the first drive-side scroll part 71 and the second driven-side wall body 92 b installed on the discharge port 3 d side from the driven-side end plate 90 a meshes with the second drive-side wall body 72 b of the second drive-side scroll part 72.
The three first driven-side wall bodies 91 b, that is, the first driven-side wall bodies 91 b in the form of three flights are provided as illustrated in FIG. 17. The driven-side wall bodies 91 b in the form of three flights are disposed at equal gaps around the driven-side rotational axis CL2. The second driven-side wall body 92 b is similar in configuration. Each of the driven- side wall bodies 91 b and 92 b may be one, two, or four or more in the number of flights.
The support member 33 is provided on the discharge port 3 d side (left side in FIG. 15) of the driven-side scroll member 90. The support member 33 is fixed by the bolt 25 to the leading edge (free end) of the second driven-side wall body 92 b.
The shank 35 a for the support member is provided on the central axis side of the support member 33 and the shank 35 a for the support member is fixed to the housing 3 via the bearing 38 for the second support member, which is a ball bearing. As a result, the driven-side scroll member 90 rotates around the driven-side rotational axis CL2 via the support member 33.
The first side plate 27 is provided on the motor 5 side (right side in FIG. 15) of the driven-side scroll member 90. The first side plate 27 is fixed by the bolt 28 to the leading edge (free end) of the first driven-side wall body 91 b. Formed at the rotation center of the first side plate 27 is the hole portion 27 h for the first side plate for penetration by the drive shaft portion 71 d.
The second side plate 30 is provided at a predetermined gap on the motor 5 side of the first side plate 27. The second side plate 30 is fixed by the bolt 34 to the first side plate 27. Formed at the rotation center of the second side plate 30 is the hole portion 30 h for the second side plate for penetration by the drive shaft portion 71 d.
The shank 30 a for the second side plate is provided on the central axis side of the second side plate 30 and the shank 30 a for the second side plate is fixed to the housing 3 via the bearing 32 for the second side plate, which is a ball bearing. As a result, the driven-side scroll member 90 rotates around the driven-side rotational axis CL2 via the second side plate 30 and the first side plate 27. The closed space that is formed between the second side plate 30 and the first side plate 27 is supplied with a lubricant such as oil and grease, and a sliding portion is lubricated as a result.
The first protruding wall portion 27 b protruding toward the second side plate 30 is provided on the outer peripheral side end surface of the first side plate 27. The second protruding wall portion 30 c protruding toward the first side plate 27 is provided on the outer peripheral side end surface of the second side plate 30. The protruding wall portions 27 b and 30 c constitute a peripheral wall portion by being attached to each other and fixed in a liquid-tight state. As a result, the center plate 20 disposed between the first side plate 27 and the second side plate 30 is accommodated in the space S surrounded by both protruding wall portions 27 b and 30 c as illustrated in FIG. 18.
As illustrated in FIG. 15, the pin ring mechanism (synchronization drive mechanism) 15 is provided between the first and second side plates 27 and 30 and the center plate 20. The pin ring mechanism 15 is provided with a round bar-shaped pin 45 and a rolling bearing (ring) 46, which guides the pin 45 by the inner peripheral surface of the rolling bearing 46 abutting against the outer periphery of the pin 45.
As illustrated in FIG. 18, three pin ring mechanisms 15 are provided at equal angular gaps around the rotation center of the center plate 20. The pin ring mechanism 15 may be four or more in number.
FIG. 19 is an enlarged view of the part around the pin ring mechanism 15.
One end (the left end) of the pin 45 is press-fitted and fixed to the first side plate 27 and the other end (right end) of the pin 45 is press-fitted and fixed to the second side plate 30. The longitudinal central portion of the pin 45 abuts against the inner peripheral surface of an inner ring 46 b of the rolling bearing 46.
The rolling bearing 46, which is a ball bearing, is fitted in a hole portion formed in the center plate 20. The rolling bearing 46 is provided with an outer ring 46 a, the inner ring 46 b, a plurality of balls (rolling members) 46 c, and a holder (not illustrated) holding each ball 46 c. A lubricant such as grease is enclosed in the rolling bearing 46.
The pin ring mechanism 15 is used as a synchronization drive mechanism transmitting a drive force from the drive shaft portion 71 d to the driven-side scroll member 90 such that both scroll members 70 and 90 relatively perform revolving and orbiting motions in synchronization.
The co-rotating scroll compressor 1 configured as described above operates as follows.
The drive shaft 6 is rotated around the drive-side rotational axis CL1 by the motor 5, and then the center plate 20 as well as the drive-side scroll member 70 rotates around the drive-side axis CL1 via the drive shaft portion 71 d connected to the drive shaft 6. By the center plate 20 rotating, the drive force transmitted to the center plate is transmitted from the first side plate 27 and the second side plate 30 to the driven-side scroll member 90 via the pin ring mechanism 15 as a synchronization drive mechanism and the driven-side scroll member 90 rotates around the driven-side rotational axis CL2. At this time, the pin ring mechanism 15 causes both scroll members 70 and 90 to relatively perform the revolving and orbiting motions.
By both scroll members 70 and 90 performing the revolving and orbiting motions, the air suctioned from the intake port of the housing 3 is suctioned from the outer peripheral sides of both scroll members 70 and 90 and taken into the compression chamber formed by both scroll members 70 and 90. Then, the compression chamber formed by the first drive-side wall body 71 b and the first driven-side wall body 91 b and the compression chamber formed by the second drive-side wall body 72 b and the second driven-side wall body 92 b are separately compressed. The air is compressed as the volume of each compression chamber decreases with a movement to the center side. The air compressed by the first drive-side wall body 71 b and the first driven-side wall body 91 b passes through the through-hole 90 h formed in the driven-side end plate 90 a and merges with the air compressed by the second drive-side wall body 72 b and the second driven-side wall body 92 b, and the merged air is discharged from the discharge port 3 d of the housing 3 to the outside through the discharge port 72 d.
The present embodiment has the following action and effect.
The pin ring mechanism 15 provided with the round bar-shaped pin 45 and the rolling bearing 46 is adopted as a synchronization drive mechanism. As a result, it is possible to realize the synchronization drive mechanism without adopting a crank pin mechanism, and thus it is possible to achieve cost reduction without a complex configuration caused by a large number of bearings being adopted as in the case of crank pin mechanisms.
The pin 45 is press-fitted and fixed to the side plates 27 and 30, and thus the pin 45 can be used as a positioning pin for both side plates 27 and 30.
Both ends of the pin 45 are fixed to both side plates 27 and 30 and the central portion of the pin 45 abuts against the inner peripheral surface of the rolling bearing 46. Accordingly, inclination of the inner ring 46 b of the rolling bearing 46 can be prevented, an oblique movement of the ball 46 c can be prevented, and the life of the synchronization drive mechanism can be extended.

Modification Example 1

The present embodiment can be modified as follows. As illustrated in FIG. 20, in a pin ring mechanism 15A of the present modification example, one end (the left end) of the pin 45 is press-fitted and fixed to the first side plate 27 as in the seventh embodiment and the other end (right end) of the pin 45 is fixed to the second side plate 30 via an O-ring (elastic body) 47.
The present modification example has the following action and effect.
One end of the pin 45 is press-fitted and fixed to the first side plate 27 and the other end of the pin 45 is fixed to the second side plate 30 via the O-ring 47. As a result, both ends of the pin 45 being incapable of being press-fitted to both side plates 27 and 30 due to a component tolerance can be prevented, assembly can be facilitated, and cost reduction can be achieved.
The O-ring 47 is provided on the second side plate 30 side in the present modification example, the O-ring 47 may be provided on the first side plate 27 side.

Modification Example 2

The pin ring mechanism 15 of the present embodiment illustrated in FIG. 19 and the pin ring mechanism 15A of Modification Example 1 illustrated in FIG. 20 may be combined with each other.
Specifically, as illustrated in FIG. 18, two out of the three pin ring mechanisms are the pin ring mechanisms 15 illustrated in FIG. 19 and the remaining one pin ring mechanism is the pin ring mechanism 15A illustrated in FIG. 20.
The present modification example has the following action and effect.
Two out of the three pin ring mechanisms have a function as a positioning pin as a configuration in which both ends of the pin 45 are press-fitted and fixed to both side plates 27 and 30. As for the pin 45 of the other pin ring mechanism, one end is press-fitted and fixed and the other end is fixed via the O-ring 47, which results in tolerance absorption. As a result, both side plates 27 and 30 can be positioned by means of the pin ring mechanism 15 and assemblability improvement can be achieved.

Eighth Embodiment

Next, an eighth embodiment of the present invention will be described. The present embodiment differs from the seventh embodiment in terms of the configuration of the pin ring mechanism. The eighth embodiment is similar to the seventh embodiment regarding the other points, and thus the points will not be described below.
As illustrated in FIG. 21, in a pin ring mechanism 15B of the present embodiment, the first side plate 27 and the second side plate 30 are provided with rolling bearings 49 and 51, respectively. The longitudinal central portion of the pin 45 is press-fitted and fixed to the center plate 20. Both ends of the pin 45 abut against the inner peripheral surfaces of the rolling bearings 49 and 51.
The present embodiment has the following action and effect.
The central portion of the pin 45 is press-fitted to the center plate 20 and both ends of the pin 45 abut against the inner peripheral surfaces of the rolling bearings 49 and 51 provided on both side plates 27 and 30. Accordingly, both ends of the pin 45 are not restrained by both side plates 27 and 30, and thus it is possible to avoid a situation in which the pin 45 cannot be fixed during assembly due to the component tolerance of both side plates 27 and 30. As a result, assemblability improvement can be achieved.
O-rings (elastic bodies) 23 may be respectively provided at both ends of the pin 45 as illustrated in FIG. 22. Then, the impact at a time when the pin 45 abuts against the inner peripheral surfaces of the rolling bearings 49 and 51 can be mitigated and noise can be reduced.
Although the rolling bearings 46, 49, and 51 are adopted as members receiving the pin 45 in the embodiments described above, a slide bearing such as a floating bush bearing may be adopted instead. For example, a slide bearing 48 may be provided instead of the rolling bearing 46 illustrated in FIG. 19 as illustrated in FIG. 23. Then, cost reduction can be achieved as compared with a case where the rolling bearing is adopted. In addition, the moment of inertia of a rotation system such as the rolling bearing can be reduced, and thus response enhancement can be achieved. Lubricant-based lubrication is required particularly in a case where the slide bearing is adopted, and thus more suitable is a liquid-tight structure in which the protruding wall portions 27 b and 30 c of both side plates 27 and 30 are attached to each other as illustrated in FIG. 15. However, such a liquid-tight structure does not limit the present invention including each of the embodiments described above.

Ninth Embodiment

Hereinafter, a ninth embodiment of the present invention will be described with reference to the drawings including FIG. 24.
FIG. 24 illustrates the co-rotating scroll compressor 1. The co-rotating scroll compressor 1 can be used as a turbocharger compressing combustion air (a fluid) supplied to an internal combustion engine such as a vehicular engine, a compressor for supplying compressed air to an air electrode of a fuel cell, or a compressor for supplying compressed air used for a braking device of a vehicle such as a railway vehicle.
The co-rotating scroll compressor 1 is provided with the housing 3, the motor (drive unit) 5 accommodated on one end side of the housing 3, and the drive-side scroll member 70 and the driven-side scroll member 90 accommodated on the other end side of the housing 3.
The housing 3 has a substantially cylindrical shape and is provided with the motor accommodation portion 3 a accommodating the motor 5 and the scroll accommodation portion 3 b accommodating the scroll members 70 and 90.
The discharge port 3 d for discharging compressed air is formed in an end portion of the scroll accommodation portion 3 b. The housing 3 is provided with an air intake port (not illustrated in FIG. 24) suctioning air.
The motor 5 is driven by power being supplied from a power supply source (not illustrated). The rotation of the motor 5 is controlled by a command from a control unit (not illustrated). The stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3. The rotor 5 b of the motor 5 rotates around the drive-side rotational axis CL1. The drive shaft 6 extending on the drive-side rotational axis CL1 is connected to the rotor 5 b. The drive shaft 6 is connected to the drive shaft portion 71 d fixed to the first drive-side scroll part 71 of the drive-side scroll member 70.
The drive-side bearing 11 rotatably supporting the drive shaft 6 is provided at the front end (left end in FIG. 24) of the drive shaft 6. The rear end bearing 17 rotatably supporting the drive shaft 6 between the housing 3 and the rear end bearing 17 is provided at the rear end (right end in FIG. 24) of the drive shaft 6, that is, in the end portion of the drive shaft 6 that is on the side opposite to the drive-side scroll member 70.
The drive-side scroll member 70 is provided with the first drive-side scroll part 71 on the motor 5 side and the second drive-side scroll part 72 on the discharge port 3 d side.
The first drive-side scroll part 71 is provided with the first drive-side end plate 71 a and the first drive-side wall body 71 b.
The first drive-side end plate 71 a extends in a direction orthogonal to the drive-side rotational axis CL1. The drive shaft portion 71 d extending on and along the drive-side rotational axis CL1 is fixed to the rotation center of the first drive-side end plate 71 a.
The center plate (a bearing support member) 20 is fixed to the drive shaft portion 71 d. The center plate 20 extends in parallel with the first drive-side end plate 71 a.
The first drive-side end plate 71 a is substantially disk-shaped in plan view. As illustrated in FIG. 25, the three spiral first drive-side wall bodies 71 b, that is, the spiral first drive-side wall bodies 71 b in the form of three flights are provided on the first drive-side end plate 71 a. The first drive-side wall bodies 71 b in the form of three flights are disposed at equal gaps around the drive-side rotational axis CL1. The first drive-side wall body 71 b may be one, two, or four or more in the number of flights.
As illustrated in FIG. 24, the second drive-side scroll part 72 is provided with the second drive-side end plate 72 a and the second drive-side wall body 72 b. The second drive-side wall body 72 b is in the form of three flights similarly to the first drive-side wall body 71 b (see FIG. 25) described above. The second drive-side wall body 72 b may be one, two, or four or more in the number of flights.
The second drive-side shaft portion 72 c extending in the drive-side rotational axis CL1 direction is connected to the second drive-side end plate 72 a. The second drive-side shaft portion 72 c is provided rotatably with respect to the housing 3 via the second drive-side bearing 14, which is a ball bearing. The second drive-side end plate 72 a is provided with the discharge port 72 d, which is along the drive-side rotational axis CL1.
The two seal members 26 for the second drive shaft portion are provided between the second drive-side shaft portion 72 c and the housing 3 and on the leading edge side (left side in FIG. 24) of the second drive-side shaft portion 72 c beyond the second drive-side bearing 14. The two seal members 26 for the second drive shaft portion and the second drive-side bearing 14 are disposed at predetermined gaps in the drive-side rotational axis CL1 direction. Enclosed between the two seal members 26 for the second drive shaft portion is a lubricant that is grease such as a semi-solid lubricant. The seal member 26 for the second drive shaft portion may be one in number. In this case, the lubricant is enclosed between the seal member 26 for the second drive shaft portion and the second drive-side bearing 14.
The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed in a state where the leading edges (free ends) of the wall bodies 71 b and 72 b face each other. The first drive-side scroll part 71 and the second drive-side scroll part 72 are fixed by the bolt 31, which is fastened to the flange portions 73 provided at a plurality of places in the circumferential direction so as to protrude to the radial outer side.
In the driven-side scroll member 90, the driven-side end plate 90 a is positioned substantially at the center in the axial direction (horizontal direction in the drawing). The through-hole 90 h is formed at the center of the driven-side end plate 90 a and compressed air flows to the discharge port 72 d.
The first driven-side wall body 91 b and the second driven-side wall body 92 b are provided on both sides of the driven-side end plate 90 a, respectively. The first driven-side wall body 91 b installed on the motor 5 side from the driven-side end plate 90 a meshes with the first drive-side wall body 71 b of the first drive-side scroll part 71 and the second driven-side wall body 92 b installed on the discharge port 3 d side from the driven-side end plate 90 a meshes with the second drive-side wall body 72 b of the second drive-side scroll part 72.
The three first driven-side wall bodies 91 b, that is, the first driven-side wall bodies 91 b in the form of three flights are provided as illustrated in FIG. 26. The driven-side wall bodies 91 b in the form of three flights are disposed at equal gaps around the driven-side rotational axis CL2. The second driven-side wall body 92 b is similar in configuration. Each of the driven- side wall bodies 91 b and 92 b may be one, two, or four or more in the number of flights.
The support member 33 is provided on the discharge port 3 d side (left side in FIG. 24) of the driven-side scroll member 90. The support member 33 is fixed by the bolt 25 to the leading edge (free end) of the second driven-side wall body 92 b.
The shank 35 a for the support member is provided on the central axis side of the support member 33 and the shank 35 a for the support member is fixed to the housing 3 via the bearing 38 for the second support member, which is an angular ball bearing. As a result, the driven-side scroll member 90 rotates around the driven-side rotational axis CL2 via the support member 33.
The first side plate (a bearing support member) 27 is provided on the motor 5 side (right side in FIG. 24) of the driven-side scroll member 90. The first side plate 27 is fixed by the bolt 28 to the leading edge (free end) of the first driven-side wall body 91 b. Formed at the rotation center of the first side plate 27 is the hole portion 27 h for the first side plate for penetration by the drive shaft portion 71 d.
The second side plate (a bearing support member) 30 is provided at a predetermined gap on the motor 5 side of the first side plate 27. The second side plate 30 is fixed by the bolt 34 to the first side plate 27. Formed at the rotation center of the second side plate 30 is the hole portion 30 h for the second side plate for penetration by the drive shaft portion 71 d.
The shank 30 a for the second side plate is provided on the central axis side of the second side plate 30 and the shank 30 a for the second side plate is fixed to the housing 3 via the bearing 32 for the second side plate, which is an angular ball bearing. As a result, the driven-side scroll member 90 rotates around the driven-side rotational axis CL2 via the second side plate 30 and the first side plate 27.
The first protruding wall portion 27 b protruding toward the second side plate 30 is provided on the outer peripheral side end surface of the first side plate 27. The second protruding wall portion 30 c protruding toward the first side plate 27 is provided on the outer peripheral side end surface of the second side plate 30. The protruding wall portions 27 b and 30 c constitute a peripheral wall portion by being attached to each other and fixed in a liquid-tight state. As a result, the center plate 20 disposed between the first side plate 27 and the second side plate 30 is accommodated in the space S surrounded by both protruding wall portions 27 b and 30 b as illustrated in FIG. 27.
As illustrated in FIG. 24, the crank pin 15 is provided between the first and second side plates 27 and 30 and the center plate 20. The crank pin 15 has the cylindrical portion 15 a at the center and the first eccentric shaft portion 15 b and a second eccentric shaft portion 15 f, which have eccentric axes which are eccentric to the central axis of the cylindrical portion 15 a. The first eccentric shaft portion 15 b protrudes to one side (the left side) of the cylindrical portion 15 a and the second eccentric shaft portion 15 f protrudes to the other side (right side) of the cylindrical portion 15 a. As a result, the crank pin 15 has a symmetrical shape about the cylindrical portion 15 a.
Provided on the outer periphery of the cylindrical portion 15 a is the bearing 16 for the cylindrical portion (a cylindrical portion rolling bearing), which is an angular ball bearing. As a result, the cylindrical portion 15 a is rotatable with respect to the center plate 20. A lubricant such as grease is enclosed in the bearing 16 for the cylindrical portion.
The first eccentric shaft portion 15 b is provided with the bearing 34 for the first eccentric shaft portion (a first crank pin end portion rolling bearing), which is an angular ball bearing. As a result, the first eccentric shaft portion 15 b is rotatable with respect to the first side plate 27. Grease (a lubricant) is enclosed in the bearing 34 for the first eccentric shaft portion.
The second eccentric shaft portion 15 f is provided with a bearing 35 for the second eccentric shaft portion (second crank pin end portion rolling bearing), which is an angular ball bearing. As a result, the second eccentric shaft portion 15 f is rotatable with respect to the second side plate 30. Grease (a lubricant) is enclosed in the bearing 35 for the second eccentric shaft portion.
The crank pin 15 and the respective bearings 16, 34, and 35 are used as synchronization drive mechanisms transmitting a drive force from the drive shaft portion 71 d to the driven-side scroll member 90 such that both scroll members 70 and 90 perform revolving and orbiting motions in synchronization.
It is preferable that a plurality of the synchronization drive mechanisms provided with the crank pin 15 are provided. For example, three synchronization drive mechanisms are provided at equal angular gaps around the rotational axes CL1 and CL2 (see FIG. 27).
FIG. 28 is an enlarged view of the part around the crank pin 15.
The bearing 16 for the cylindrical portion is provided with an outer ring 16 a, an inner ring 16 b, balls 16 c disposed between the outer ring 16 a and the inner ring 16 b, and a holder (not illustrated) holding the respective balls 16 c at equal gaps.
The outer ring 16 a is fitted to a circular groove formed in the center plate 20 via an O-ring (elastic body) 36. The O-ring 36 is disposed in a state where the O-ring 36 is deformed by a predetermined amount and the O-ring 36 presses the outer ring 16 a in the inner ring 16 b direction.
The inner ring 16 b is press-fitted and fitted to the cylindrical portion 15 a.
A seal member 52 for sealing a lubricant is provided on a side (the right side in FIG. 28) of the bearing 16 for the cylindrical portion. The seal member 52 has an annular shape and the outer peripheral side of the seal member 52 is fixed to a side portion of the outer ring 16 a. The seal member 52 is not fixed to the inner ring 16 b and a predetermined gap is provided with respect to a side portion of the inner ring 16 b. The inner peripheral end of the seal member 52 extends to the side portion of the inner ring 16 b. More specifically, the inner peripheral end of the seal member 52 extends to the inner peripheral side beyond the outer periphery of the inner ring 16 b.
A snap ring 55 for fixing the seal member 52 in place is provided on a side (the right side in the drawing) of the seal member 52.
The bearing 34 for the first eccentric shaft portion is provided with an outer ring 34 a, an inner ring 34 b, a plurality of balls 34 c disposed between the outer ring 34 a and the inner ring 34 b, and a holder (not illustrated) holding the respective balls 34 c at equal gaps.
The outer ring 34 a is fitted by press-fitting to a circular groove formed in the first side plate 27. The inner ring 34 b is fitted to the first eccentric shaft portion 15 b by press-fitting.
A seal member 53 for sealing a lubricant is provided on a side (the right side in FIG. 28) of the bearing 34 for the first eccentric shaft portion. The seal member 53 has an annular shape and the outer peripheral side of the seal member 53 is fixed to a side portion of the outer ring 34 a. The seal member 53 is not fixed to the inner ring 34 b and a predetermined gap is provided with respect to a side portion of the inner ring 34 b. The inner peripheral end of the seal member 53 extends to the side portion of the inner ring 34 b. More specifically, the inner peripheral end of the seal member 53 extends to the inner peripheral side beyond the outer periphery of the inner ring 34 b.
A snap ring 56 for fixing the seal member 53 in place is provided on a side (the right side in the drawing) of the seal member 53.
The bearing 35 for the second eccentric shaft portion is provided with an outer ring 35 a, an inner ring 35 b, a plurality of balls 35 c disposed between the outer ring 35 a and the inner ring 35 b, and a holder (not illustrated) holding the respective balls 35 c at equal gaps.
The outer ring 35 a is fitted by press-fitting to a circular groove formed in the second side plate 30. The inner ring 35 b is fitted to the second eccentric shaft portion 15 f by press-fitting.
A seal member 54 for sealing a lubricant is provided on a side (the left side in FIG. 28) of the bearing 35 for the second eccentric shaft portion. The seal member 54 has an annular shape and the outer peripheral side of the seal member 54 is fixed to a side portion of the outer ring 35 a. The seal member 54 is not fixed to the inner ring 35 b and a predetermined gap is provided with respect to a side portion of the inner ring 35 b. The inner peripheral end of the seal member 54 extends to the side portion of the inner ring 35 b. More specifically, the inner peripheral end of the seal member 54 extends to the inner peripheral side beyond the outer periphery of the inner ring 35 b.
A snap ring 57 for fixing the seal member 54 in place is provided on a side (the right side in the drawing) of the seal member 54.
The co-rotating scroll compressor 1 configured as described above operates as follows.
The drive shaft 6 is rotated around the drive-side rotational axis CL1 by the motor 5, and then the center plate 20 as well as the drive-side scroll member 70 rotates around the drive-side axis CL1 via the drive shaft portion 71 d connected to the drive shaft 6. By the center plate 20 rotating, the drive force transmitted to the center plate is transmitted from the first side plate 27 and the second side plate 30 to the driven-side scroll member 90 via the crank pin 15 as a synchronization drive mechanism and the driven-side scroll member 90 rotates around the driven-side rotational axis CL2. At this time, the crank pin 15 rotates with respect to the center plate 20 and both side plates via the respective bearings 16, 34, and 35, and thus both scroll members 70 and 90 relatively perform the revolving and orbiting motions.
By both scroll members 70 and 90 performing the revolving and orbiting motions, the air suctioned from the intake port of the housing 3 is suctioned from the outer peripheral sides of both scroll members 70 and 90 and taken into the compression chamber formed by both scroll members 70 and 90. Then, the compression chamber formed by the first drive-side wall body 71 b and the first driven-side wall body 91 b and the compression chamber formed by the second drive-side wall body 72 b and the second driven-side wall body 92 b are separately compressed. The air is compressed as the volume of each compression chamber decreases with a movement to the center side. The air compressed by the first drive-side wall body 71 b and the first driven-side wall body 91 b passes through the through-hole 90 h formed in the driven-side end plate 90 a and merges with the air compressed by the second drive-side wall body 72 b and the second driven-side wall body 92 b, and the merged air is discharged from the discharge port 3 d of the housing 3 to the outside through the discharge port 72 d.
The present embodiment has the following action and effect.
As illustrated in FIG. 28, the O-ring 36 is provided between the center plate 20 and the outer ring 16 a of the bearing 16 for the cylindrical portion. As a result, the tolerance of the crank pin 15, the side plates 27 and 30, and the center plate 20 can be absorbed by the O-ring 36 being deformed, internal force generation in the crank pin 15 can be avoided, and the life of the synchronization drive mechanism can be extended.
In addition, the machining tolerance of the crank pin 15 can be mitigated and machining and management costs can be reduced.
In addition, the outer ring 16 a is pressed to the inner ring 16 b side by the O-ring 36, and thus it is possible to prevent slipping between the outer ring 16 a and the hole in which the outer ring 16 a is fitted.
The outer ring 34 a of the bearing 34 for the first eccentric shaft portion and the outer ring 35 a of the bearing 35 for the second eccentric shaft portion are press-fitted, and thus the centrifugal force around the rotational axes CL1 and CL2 is held by the bearings 34 and 35 for the eccentric shaft portions. The two bearings 34 and 35 bear the centrifugal force in this manner, and thus the load to be borne can be mitigated as compared with a case where the single bearing 16 for the cylindrical portion bears the centrifugal force.
In addition, the crank pin 15 is supported at both ends by the two bearings 34 and 35 for the eccentric shaft portions, and thus the posture of the crank pin 15 can be stabilized.

Modification Example 1

The present embodiment can be modified as follows. The outer ring 16 a of the bearing 16 for the cylindrical portion may be press-fitted and the outer rings 34 a and 35 a of both bearings 34 and 35 for the eccentric shaft portions may be provided with an O-ring 37 as illustrated in FIG. 29.
Then, the tolerance of the crank pin 15, the side plates 27 and 30, and the center plate 20 can be absorbed by the O-ring 37 being deformed, internal force generation in the crank pin 15 can be avoided, and the life of the synchronization drive mechanism can be extended.
In addition, the machining tolerance of the crank pin 15 can be mitigated and machining and management costs can be reduced.
In addition, the outer ring 16 a is pressed to the inner ring 16 b side by the O-ring 36, and thus it is possible to prevent slipping between the outer ring 16 a and the hole in which the outer ring 16 a is fitted.

Modification Example 2

The present embodiment can be modified as follows. The outer rings 34 a and 35 a of both bearings 34 and 35 for the eccentric shaft portions may be provided with the O-ring 37 with the outer ring 16 a of the bearing 16 for the cylindrical portion provided with the O-ring 36 as illustrated in FIG. 30.
Then, the tolerance of the crank pin 15, the side plates 27 and 30, and the center plate 20 can be absorbed by the O- rings 36 and 37 being deformed, internal force generation in the crank pin 15 can be avoided, and the life of the synchronization drive mechanism can be extended.
In addition, the machining tolerance of the crank pin 15 can be mitigated and machining and management costs can be reduced.
In addition, the outer ring 16 a is pressed to the inner ring 16 b side by the O-ring 36, and thus it is possible to prevent slipping between the outer ring 16 a and the hole in which the outer ring 16 a is fitted.

Modification Example 3

The present embodiment can be modified as follows.
The outer ring 16 a of the bearing 16 for the cylindrical portion and the outer rings 34 a and 35 a of both bearings 34 and 35 for the eccentric shaft portions may be press-fitted and an O-ring 38 may be provided between the crank pin 15 and each of the inner rings 16 b, 34 b, and 35 b as illustrated in FIG. 31.
Then, the tolerance of the crank pin 15, the side plates 27 and 30, and the center plate 20 can be absorbed by the O-ring 38 being deformed, internal force generation in the crank pin 15 can be avoided, and the life of the synchronization drive mechanism can be extended.
In addition, the machining tolerance of the crank pin 15 can be mitigated and machining and management costs can be reduced.
The O-ring 38 may be provided only between the crank pin 15 and the inner ring 16 b of the bearing 16 for the cylindrical portion or only between the crank pin 15 and the inner rings 34 b and 35 b of both bearings 34 and 35 for the eccentric shaft portions.

Tenth Embodiment

Next, a tenth embodiment of the present invention will be described. The present embodiment differs from the ninth embodiment in terms of the configuration of the crank pin 15. The tenth embodiment is similar to the ninth embodiment regarding the other points, and thus the points will not be described below.
As illustrated in FIG. 32A, the components including the cylindrical portion 15 a and an eccentric shaft portion 15 g constitute a crank pin 15′. The first eccentric shaft portion 15 b and the second eccentric shaft portion 15 f are provided at both ends of the eccentric shaft portion 15 g, respectively.
An insertion hole 15 a 1 into which the eccentric shaft portion 15 g is inserted is formed in the cylindrical portion 15 a. The eccentric shaft portion 15 g is fixed by being press-fitted into the insertion hole 15 a 1.
The crank pin 15 illustrated in the ninth embodiment is illustrated in FIG. 32B. The cylindrical portion 15 a, the first eccentric shaft portion 15 b, and the second eccentric shaft portion 15 f are integrated in the crank pin 15 formed by being cut out from the same material.
The present embodiment has the following action and effect.
The eccentric shaft portion 15 g of the crank pin 15′ is inserted into the insertion hole 15 a 1 formed in the cylindrical portion 15 a. As a result, the eccentric shaft portion 15 g and the cylindrical portion 15 a can be separate components and can be machined separately. Accordingly, the axial centers of the first eccentric shaft portion 15 b and the second eccentric shaft portion 15 f at both ends of the eccentric shaft portion 15 g can be aligned as compared with a case where the eccentric shaft portion 15 g and the cylindrical portion 15 a are integrally machined (FIG. 32B). Accordingly, an internal force applied to the crank pin 15′ can be reduced and the life of the synchronization drive mechanism can be extended.
Although the crank pin 15′ of the present embodiment can be applied in place of the crank pin 15 of the ninth embodiment, the crank pin 15′ of the present embodiment is not limited to the configuration of the ninth embodiment and can be applied as a crank pin used in a co-rotating scroll compressor.

REFERENCE SIGNS LIST

- 1 Co-rotating scroll compressor
- 3 Housing
- 3 a Motor accommodation portion
- 3 b Scroll accommodation portion
- 3 d Discharge port
- 5 Motor (drive unit)
- 5 a Stator
- 5 b Rotor
- 6 Drive shaft
- 11 Drive-side bearing
- 15 Crank pin (synchronization drive mechanism)
- 15 a Cylindrical portion
- 15 a 1 Insertion hole
- 15 b Eccentric shaft portion, first eccentric shaft portion
- 15 c End portion
- 15 d Small-diameter portion
- 15 e Central portion
- 15 f Second eccentric shaft portion
- 15 g Eccentric shaft portion
- 16 Bearing for cylindrical portion
- 17 Rear end bearing
- 18 a Bearing for first eccentric shaft portion (crank pin end portion rolling bearing)
- 18 b Bearing for second eccentric shaft portion (crank pin end portion rolling bearing)
- 19 O-ring (urging member)
- 20 Center plate
- 20 a Shank
- 20 b Fixing portion
- 21 Bolt
- 22 O-ring (elastic body)
- 23 O-ring (elastic body)
- 25 Bolt
- 26 Seal member
- 27 First side plate
- 27 a Fixing portion
- 27 b First protruding wall portion
- 27 h Hole portion for first side plate
- 28 Bolt
- 30 Second side plate
- 30 a Shank for second side plate
- 30 b Fixing portion
- 30 c Second protruding wall portion
- 30 d Drive shaft portion
- 30 h Hole portion for second side plate
- 31 Bolt
- 32 Bearing for second side plate
- 33 Support member
- 34 Bearing for first eccentric shaft portion (first crank pin end portion rolling bearing)
- 34 a Outer ring
- 34 b Inner ring
- 34 c Ball
- 35 Bearing for second eccentric shaft portion (second crank pin end portion rolling bearing)
- 35 a Outer ring
- 35 b Inner ring
- 35 c Ball
- 36, 37, 38 O-ring (elastic body)
- 40 Resinous shaft portion (resin portion)
- 41 Seal plate
- 42 Stopper ring
- 43 First seal member
- 44 Second seal member
- 45 Pin
- 46 Rolling bearing (ring)
- 46 a Outer ring
- 46 b Inner ring
- 46 c Ball (rolling member)
- 47 O-ring (elastic body)
- 48 Slide bearing
- 49 Rolling bearing
- 50 Drive-side scroll member
- 51 Rolling bearing
- 52, 53, 54 Seal member
- 55, 56, 57 Snap ring
- 60 Driven-side scroll member
- 61 a First driven-side end plate
- 61 d Driven shaft portion
- 70 Drive-side scroll member
- 71 First drive-side scroll part
- 71 a First drive-side end plate
- 71 b First drive-side wall body
- 71 d Drive shaft portion
- 72 Second drive-side scroll part
- 72 a Second drive-side end plate
- 72 b Second drive-side wall body
- 72 c Second drive-side shaft portion
- 72 d Discharge port
- 73 Flange portion
- 90 Driven-side scroll member
- 90 h Through-hole
- 91 First driven-side scroll part
- 91 b First driven-side wall body
- 92 b Second driven-side wall body
- CL1 Drive-side rotational axis
- CL2 Driven-side rotational axis
- CL3 Eccentric axis
- t Gap
- S Space

Claims

1. A co-rotating scroll compressor comprising:

a drive-side scroll member driven to rotate around a rotational axis by a drive unit and having a spiral drive-side wall body disposed on a drive-side end plate;

a driven-side scroll member in which a spiral driven-side wall body corresponding to the drive-side wall body is disposed on a driven-side end plate and the driven-side wall body meshes with the drive-side wall body to form a compression space;

a synchronization drive mechanism transmitting a drive force of the drive unit to the driven-side scroll member such that the drive-side scroll member and the driven-side scroll member perform rotating motions in the same direction and at the same angular velocity;

a first side plate disposed on the rotational axis direction side with respect to the drive-side scroll member and the driven-side scroll member;

a second side plate fixed at a predetermined gap in the rotational axis direction with respect to the first side plate; and

a center plate disposed between the first side plate and the second side plate, wherein

the first side plate is fixed to one of the drive-side scroll member and the driven-side scroll member,

the center plate is fixed to the other of the drive-side scroll member and the driven-side scroll member, and

the synchronization drive mechanism is provided between the first and second side plates and the center plate.

2. The co-rotating scroll compressor according to claim 1, wherein

the synchronization drive mechanism is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion and a crank pin end portion rolling bearing provided between both end portions of the eccentric shaft portion and the first and second side plates, and

an urging member urging an inner ring of the crank pin end portion rolling bearing toward a leading edge of the eccentric shaft portion in the eccentric axis direction is provided between the inner ring and the eccentric shaft portion.

3. The co-rotating scroll compressor according to claim 1, wherein

a preload is applied to the crank pin end portion rolling bearing in the eccentric axis direction by a gap between the first side plate and the second side plate.

4. The co-rotating scroll compressor according to claim 1, wherein

an elastic body is provided between an inner peripheral surface of an inner ring of the crank pin end portion rolling bearing and an outer peripheral surface of the eccentric shaft portion.

5. The co-rotating scroll compressor according to claim 1, wherein among a fixing portion of the first side plate which is fixed to one of the drive-side scroll member and the driven-side scroll member and a fixing portion of the center plate which is fixed to the other of the drive-side scroll member and the driven-side scroll member, the fixing portion positioned on a radial inner side of a center of the scroll member has a structure in which a resin portion is interposed, and the fixing portion positioned on a radial outer side of the center of the scroll member has a structure using a metal portion without resin portion interposition.

6. The co-rotating scroll compressor according to claim 1, wherein a peripheral wall portion surrounding an outer peripheral side of the center plate is provided between the first side plate and the second side plate.

7. The co-rotating scroll compressor according to claim 6, further comprising

a drive shaft portion rotating around the rotational axis and connected between the drive-side end plate and the drive unit, wherein

the center plate is fixed to the drive shaft portion,

a hole portion for the first side plate through which the drive shaft portion passes is formed in the first side plate,

a hole portion for the second side plate through which the drive shaft portion passes is formed in the second side plate, and

a first seal member is provided between the hole portion for the first side plate and the drive shaft portion and/or between the hole portion for the second side plate and the drive shaft portion.

8. The co-rotating scroll compressor according to claim 6, further comprising

the center plate is fixed to the drive shaft portion,

a second seal member is provided between the first side plate and the center plate and/or between the second side plate and the center plate.

9. The co-rotating scroll compressor according to claim 6, wherein

the first side plate is fixed to the drive-side wall body on an outer peripheral side,

the second side plate is fixed to the first side plate,

the drive unit is connected to a rotation center of the second side plate,

the center plate is fixed to a driven shaft portion connected to a rotation center of the driven-side end plate,

a hole portion for the first side plate through which the driven shaft portion passes is formed in the first side plate, and

a rotation center region of the second side plate is closed by a wall portion.

10. The co-rotating scroll compressor according to claim 1, wherein the synchronization drive mechanism is provided with a round bar-shaped pin provided between the first and second side plates and the center plate and a ring guiding the pin by an inner peripheral surface of the ring abutting against an outer periphery of the pin.

11. The co-rotating scroll compressor according to claim 10, wherein

the ring is a rolling bearing provided on the center plate, and

both ends of the pin are press-fitted to the first side plate and the second side plate and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing.

12. The co-rotating scroll compressor according to claim 10, wherein

the ring is a rolling bearing provided on the center plate, and

one end of the pin is press-fitted to one of the first side plate and the second side plate, the other end of the pin is fixed to the other of the first side plate and the second side plate via an elastic body, and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing.

13. The co-rotating scroll compressor according to claim 10, wherein

three or more synchronization drive mechanisms are provided to be spaced apart in a circumferential direction of the rotational axis,

in two of the synchronization drive mechanisms, the ring is a rolling bearing provided on the center plate, both ends of the pin are press-fitted to the first side plate and the second side plate, and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing, and

in the other synchronization drive mechanism, the ring is a rolling bearing provided on the center plate, one end of the pin is press-fitted to one of the first side plate and the second side plate, the other end of the pin is fixed to the other of the first side plate and the second side plate via an elastic body, and a longitudinal central portion of the pin abuts against an inner peripheral surface of the rolling bearing.

14. The co-rotating scroll compressor according to claim 10, wherein

the ring is a rolling bearing provided on each of the first side plate and the second side plate, and

a longitudinal central portion of the pin is press-fitted to the center plate and both ends of the pin abut against an inner peripheral surface of the rolling bearing.

15. The co-rotating scroll compressor according to claim 11, wherein

the ring is a slide bearing instead of the rolling bearing.

16. The co-rotating scroll compressor according to claim 1, wherein

the synchronization drive mechanism is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion, a first crank pin end portion rolling bearing provided between one end of the eccentric shaft portion and the first side plate, a second crank pin end portion rolling bearing provided between the other end of the eccentric shaft portion and the second side plate, and a cylindrical portion rolling bearing provided between the cylindrical portion and the center plate, and

an elastic body is provided in at least one of spaces between an outer ring of the first crank pin end portion rolling bearing and the first side plate, between an outer ring of the second crank pin end portion rolling bearing and the second side plate, and between an outer ring of the cylindrical portion rolling bearing and the center plate or in at least one of spaces between an inner ring of the first crank pin end portion rolling bearing and the one end of the eccentric shaft portion, between an inner ring of the second crank pin end portion rolling bearing and the other end of the eccentric shaft portion, and between an inner ring of the cylindrical portion rolling bearing and the cylindrical portion.

17. The co-rotating scroll compressor according to claim 16, wherein

the elastic body is provided between the outer ring of the cylindrical portion rolling bearing and the center plate,

the outer ring of the first crank pin end portion rolling bearing is press-fitted to the first side plate, and

the outer ring of the second crank pin end portion rolling bearing is press-fitted to the second side plate.

18. The co-rotating scroll compressor according to claim 16, wherein

an insertion hole into which the eccentric shaft portion is inserted is formed in the cylindrical portion.

19. The co-rotating scroll compressor according to claim 1, wherein

the synchronization drive mechanism is provided with a crank pin having an eccentric shaft portion having an eccentric axis which is eccentric to a central axis of a central cylindrical portion, and