JP6787864B2 - Double rotation scroll type compressor - Google Patents

Description

The present invention relates to a double rotation scroll type compressor.

Conventionally, a double-rotation scroll type compressor has been known (see Patent Document 1). This includes a drive-side scroll and a driven-side scroll that rotates synchronously with the drive-side scroll, and the driven shaft that supports the rotation of the driven-side scroll is divided by the turning radius with respect to the drive shaft that rotates the drive-side scroll. The drive shaft and the driven shaft are rotated in the same direction at the same angular velocity by offsetting only by.

Patent Document 2 discloses a scroll type compressor having a fixed scroll and a swivel scroll, unlike a double rotation scroll type compressor. A crank pin mechanism equipped with a crank pin and a ball bearing is adopted as a rotation prevention mechanism for the swivel scroll.

Japanese Patent No. 5443132 Japanese Unexamined Patent Publication No. 2005-233042

The double-rotation scroll type compressor uses a synchronous drive mechanism that transmits a driving force from the driving side scroll member to the driven side scroll member so that the driving side scroll member and the driven side scroll member rotate in the same direction at the same angular velocity. Be done. As this synchronous drive mechanism, a mechanism using a crank pin or a pin ring equipped with a rolling bearing can be considered. However, if the lubricant enclosed in the rolling bearing leaks to the outside due to centrifugal force, the bearing may be insufficiently lubricated. There is a risk of shortening the life of the bearing. Further, if the lubricant leaks to the outside, it may be mixed with the fluid before or after compression to contaminate the fluid.

In addition, the present inventors have found that in a double-rotation scroll type compressor, not only a rotation motion but also a revolution motion is applied to the rolling bearing, so that there are the following peculiar problems regarding the leakage of the lubricant of the rolling bearing. It was.

FIG. 13 shows three ball bearings (rolling bearings) 102 attached to the bearing support member 100. The bearing support member 100 rotates around the rotation center O1 together with the driving side scroll member or the driven side scroll member. In the ball bearing 102, the outer ring 102a is fitted to the bearing support member 100, and the inner ring 102b is fitted to the shaft portion 104 of the crank pin. A plurality of balls 102c are arranged between the outer ring 102a and the inner ring 102b, and a predetermined interval between the balls 102c is maintained by a cage (not shown).

When the bearing support member 100 rotates (revolves) around the center of rotation O1, centrifugal force acts in the direction indicated by the arrow of reference numeral A0, and grease (lubricant) moves outward in the radial direction as indicated by reference numeral A1. After that, as indicated by the arrow of reference numeral A2, the grease is agitated by the rotation of the ball 102c around the rotation center O2 of the shaft portion 104 and the cage. Then, as indicated by the arrow of reference numeral A3, when the grease reaches the inside in the radial direction, the grease is scattered by the centrifugal force due to the revolution, and the grease adheres to the inner ring 102b. When the grease adhering to the inner ring 102b is located on the outer side in the radial direction, the grease leaks to the outside of the ball bearing 102 from the gap on the inner ring side as shown by the arrow of the symbol A4 due to the centrifugal force due to the revolution.

Grease leaking from the inner ring side of the ball bearing 102 due to the centrifugal force due to revolution is an event that cannot occur in a scroll type compressor provided with a fixed scroll and a swivel scroll as in Patent Document 2. If grease leaks from the ball bearing 102 and the lubricant is insufficient, the ball bearing 102 becomes poorly lubricated, which hinders the extension of life.

The present invention has been made in view of such circumstances, and an object of the present invention is to provide a double-rotation scroll type compressor capable of extending the life of a synchronous drive mechanism provided with rolling bearings.

In order to solve the above problems, the double-rotation scroll type compressor of the present invention employs the following means.

That is, the double-rotation scroll type compressor according to the present invention is rotationally driven around the rotation axis by a drive unit, and has a drive-side scroll member having a spiral drive side wall arranged on the drive-side end plate, and the drive. A driven side scroll member in which a spiral driven side wall corresponding to the side wall is arranged on the driven side end plate and the driven side wall is meshed with the driving side wall to form a compression space, and the above-mentioned The drive-side scroll member and the driven-side scroll member are provided with a synchronous drive mechanism that transmits a driving force from the drive-side scroll member to the driven-side scroll member so that the driven-side scroll member rotates in the same direction at the same angular speed. The mechanism includes a crank pin and a rolling bearing that rotatably supports the shaft portion of the crank pin, and the rolling bearing is formed on an inner ring fitted to the shaft portion and a bearing support member that supports the shaft portion. It is provided with a fitted outer ring, and a seal member extending to the side portion of the inner ring is fixed to the side portion of the outer ring, and between the inner peripheral end of the seal member and the side portion of the inner ring. , It is characterized in that a predetermined gap is provided.

Since the outer ring of the rolling bearing is fitted to the bearing support member, it rotates together with the bearing support member and revolves around a predetermined central axis. Since the seal member is fixed to the outer ring, it revolves around a predetermined central axis like the outer ring. On the other hand, the inner ring of the rolling bearing not only revolves together with the outer ring, but also rotates around the central axis of the shaft portion together with the shaft portion because it is fitted to the shaft portion of the crank pin. As a result, the lubricant attracted to the inner peripheral side of the outer ring due to the centrifugal force due to the revolutionary motion may leak from the outer peripheral side of the inner ring to the outside of the rolling bearing due to the rotation of the inner ring. On the other hand, since the seal member extends to the side portion of the inner ring, it is possible to prevent the lubricant from leaking from the inner ring side to the outside of the rolling bearing. As a result, it is possible to prevent poor lubrication due to leakage of lubricating oil and extend the life of the synchronous drive mechanism.

Further, in the double-rotation scroll type compressor of the present invention, the seal member has an inner peripheral edge facing the side portion of the inner ring, and the distance from the side portion of the inner ring increases toward the inner peripheral side of the seal member. It is a feature that an inclined surface is formed.

Even if the lubricant leaks from the inner peripheral side of the seal member, an inclined surface is formed in which the distance from the side of the inner ring increases toward the inner peripheral side of the seal member, so that the revolutionary motion is centrifugal. The lubricant leaked along the crankshaft by force can be effectively received.
As the inclined surface, for example, a chamfered C surface or R surface is used.
The inclined surface may be provided over the entire circumference of the inner peripheral edge of the seal member.

Further, in the double-rotation scroll type compressor of the present invention, the inclined surface is formed only on the outer peripheral side of the revolving motion of the rolling bearing in the inner peripheral edge of the sealing member.

It was decided that the inclined surface formed on the inner peripheral edge of the seal member should be formed only on the outer peripheral side of the revolving motion of the rolling bearing. As a result, the lubricant leaked by the centrifugal force due to the revolutionary motion of the outer ring can be received by the inclined surface formed on the outer peripheral side. On the other hand, since the inclined surface is not provided on the inner peripheral side of the revolution motion, the leakage of the lubricant can be prevented as much as possible.
The range in which the inclined surface is provided is, for example, a range of 90 °, that is, 180 ° on both sides around the direction of centrifugal force due to the revolution motion.

Further, in the double-rotation scroll type compressor of the present invention, the crank pin has a diameter larger than that of the first shaft portion which is connected to the first shaft portion to which the inner ring is fitted and the first shaft portion. From a position where the stepped portion for partitioning the first shaft portion and the second shaft portion is opposed to the inner peripheral end of the seal member or a position facing the inner peripheral end. Is also characterized in that it is provided at a position far from the side portion of the inner ring.

The stepped portion that separates the first shaft portion and the second shaft portion of the crank pin is located farther from the side of the inner ring than the position facing the inner peripheral coal of the seal member or the position facing the inner peripheral end. It was decided to provide it. As a result, the lubricant leaked from the rolling bearing can be guided to the first shaft portion having a diameter smaller than that of the second shaft portion, and the lubricating oil can be received from between the seal member and the inner ring.

Further, in the double rotation scroll type compressor of the present invention, a drive side scroll member having a spiral drive side wall body which is rotationally driven around the rotation axis by a drive unit and arranged on the drive side end plate, and the drive side wall. A spiral driven side wall corresponding to the body is arranged on the driven side end plate, and the driven side scroll member forms a compression space by engaging the driven side wall with respect to the driving side wall, and the driving. The synchronous drive mechanism includes a synchronous drive mechanism that transmits a driving force from the drive side scroll member to the driven side scroll member so that the side scroll member and the driven side scroll member rotate in the same direction at the same angular speed. Includes a crank pin and a rolling bearing that rotatably supports the shaft portion of the crank pin, and the rolling bearing is fitted into an inner ring fitted to the shaft portion and a bearing support member that supports the shaft portion. A sealed member extending to the side portion of the outer ring is fixed to the side portion of the inner ring, and a predetermined seal member is provided between the outer peripheral end of the seal member and the side portion of the outer ring. It is characterized in that a gap is provided.

Since the outer ring of the rolling bearing is fitted to the bearing support member, it rotates together with the bearing support member and revolves around a predetermined central axis. On the other hand, the inner ring of the rolling bearing not only revolves together with the outer ring, but also rotates around the central axis of the shaft portion together with the shaft portion because it is fitted to the shaft portion of the crank pin. As a result, the lubricant attracted to the inner peripheral side of the outer ring due to the centrifugal force due to the revolutionary motion may leak from the outer peripheral side of the inner ring to the outside of the rolling bearing due to the rotation of the inner ring. On the other hand, since the seal member is fixed to the side portion of the inner ring and extends to the side portion of the outer ring, it is possible to prevent the lubricant from leaking from the inner ring side to the outside of the rolling bearing.

Further, in the double-rotation scroll type compressor of the present invention, a side wall portion connected to the bearing support member and provided so as to surround the outer peripheral side of the seal member is provided on the side of the seal member. It is characterized by that.

On the side of the seal member, a side wall portion is provided so as to be connected to the bearing support member and surround the outer peripheral side of the seal member. As a result, the lubricant leaked to the outer peripheral side of the rolling bearing due to the centrifugal force of the revolving motion can be retained. Further, the inner ring of the rolling bearing rotates around the central axis of the shaft portion of the crank pin due to its rotation, so that the lubricant tends to leak from the outer peripheral side of the seal member. However, the frictional force against the lubricant between the seal member and the side wall is smaller than the frictional force that tries to scrape out the lubricant by the rolling member (ball) or cage provided between the inner ring and the outer ring. Therefore, the amount of the lubricant leaking from the outer peripheral side of the sealing member to the side wall portion is small.

Further, in the double rotation scroll type compressor of the present invention, a drive side scroll member having a spiral drive side wall body which is rotationally driven around the rotation axis by a drive unit and arranged on the drive side end plate, and the drive side wall. A spiral driven side wall corresponding to the body is arranged on the driven side end plate, and the driven side scroll member forms a compression space by engaging the driven side wall with respect to the driving side wall, and the driving. The synchronous drive mechanism includes a synchronous drive mechanism that transmits a driving force from the drive side scroll member to the driven side scroll member so that the side scroll member and the driven side scroll member rotate in the same direction at the same angular speed. Is provided with a crank pin and a rolling bearing that rotatably supports the shaft portion of the crank pin, and is arranged on the outer peripheral side of the rolling bearing with respect to the central axis of the shaft portion of the crank pin. It is characterized in that a chip seal for sealing the space on the rolling bearing side is provided between the wall portion facing the surface and the wall portion facing the rolling bearing.

Since it is decided to provide a chip seal that seals the space on the rolling bearing side, the lubricant leaking from the rolling bearing can be sealed. Further, since the lubricant can be sealed in the space on the rolling bearing side, it is possible to prevent the fluid before and after compression from being contaminated with the lubricant.

Further, the double-rotation scroll type compressor of the present invention includes a snap ring provided on the side of the seal member and fixing the seal member, and the snap ring has a substantially C shape having one open portion. The open portion is arranged so as to face the rotation center of the bearing support member.

The snap ring has a substantially C shape and is fitted into the groove by urging it in a direction in which its own diameter increases. The snap ring has one open portion for reducing its own diameter at the time of attachment, and is provided with a retaining ring at each end thereof, for example, for inserting a attachment jig. Since the snap ring has an open portion, the weight on the open portion side is relatively light, and the weight on the opposite side of the open portion is heavy. Therefore, when centrifugal force is applied to the snap ring, the opposite side of the open portion tends to move in the direction of centrifugal force. In consideration of this, the open portion of the snap ring is oriented toward the center of rotation of the bearing support member. As a result, it is possible to prevent the snap ring from rotating due to centrifugal force and the seal member from shifting and sliding, and the seal member can be securely fixed.

Further, in the double rotation scroll type compressor of the present invention, a drive side scroll member having a spiral drive side wall body which is rotationally driven around the rotation axis by a drive unit and arranged on the drive side end plate, and the drive side wall. A spiral driven side wall corresponding to the body is arranged on the driven side end plate, and the driven side scroll member forms a compression space by engaging the driven side wall with respect to the driving side wall, and the driving. The synchronous drive mechanism includes a synchronous drive mechanism that transmits a driving force from the drive side scroll member to the driven side scroll member so that the side scroll member and the driven side scroll member rotate in the same direction at the same angular speed. Includes a crank pin and a rolling bearing that rotatably supports the shaft portion of the crank pin, and the rolling bearing is fitted into an inner ring fitted to the shaft portion and a bearing support member that supports the shaft portion. A sealing wall portion is provided on the side portion of the rolling bearing, which is fixed to the bearing support portion and seals the rolling bearing from the side, and the sealing wall portion is provided with an combined outer ring. It is characterized in that a recess formed from the outer ring toward the side and formed in an annular shape corresponding to the outer ring is provided.

Since the outer ring of the rolling bearing is fitted to the bearing support member, it rotates together with the bearing support member and revolves around a predetermined central axis. On the other hand, the inner ring of the rolling bearing not only revolves together with the outer ring, but also rotates around the central axis of the shaft portion together with the shaft portion because it is fitted to the shaft portion of the crank pin. As a result, the lubricant attracted to the inner peripheral side of the outer ring due to the centrifugal force due to the revolving motion may leak from the outer peripheral side of the inner ring to the outside of the rolling bearing at the time of the inner ring. On the other hand, it was decided to provide a sealing wall portion for sealing the rolling bearing from the side to suppress leakage of the lubricant from the rolling bearing. Further, the sealing wall portion is provided with a recess formed from the outer ring toward the side, and this recess is used as an oil pocket to temporarily hold the lubricant leaked from the rolling bearing. As a result, even if the lubricant leaks from the recess located above when stopped, it will be collected in the recess located below.

Leakage of lubricating oil for rolling bearings can be suppressed to extend the life of the synchronous drive mechanism.

It is a vertical sectional view which showed the double rotation scroll type compressor which concerns on 1st Embodiment of this invention. It is a top view which showed the 1st drive side wall body of FIG. It is a top view which showed the 1st driven side wall body of FIG. It is a vertical cross-sectional view which showed around the eccentric shaft part of a crank pin. It is a vertical cross-sectional view which showed the modification 1 of the 1st Embodiment. It is a vertical cross-sectional view which showed the modification 2 of the 1st Embodiment. It is a vertical sectional view which showed the reference example of the modification 3 of the 1st Embodiment. It is a vertical cross-sectional view which showed the modification 3 of the 1st Embodiment. It is a vertical cross-sectional view which showed around the eccentric shaft part of the crankpin of the double rotation scroll type compressor which concerns on 2nd Embodiment of this invention. It is a vertical cross-sectional view which showed around the eccentric shaft part of the crankpin of the double rotation scroll type compressor which concerns on 3rd Embodiment of this invention. It is a front view which showed the arrangement of the snap ring of the double rotation scroll type compressor which concerns on 4th Embodiment of this invention. It is a vertical cross-sectional view which showed around the eccentric shaft part of the crankpin of the double rotation scroll type compressor which concerns on 5th Embodiment of this invention. It is a front view which showed the process of the lubricant leaking from a ball bearing.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.
[First Embodiment]
Hereinafter, the first embodiment of the present invention will be described with reference to FIG. 1 and the like.
FIG. 1 shows a double-rotation scroll type compressor 1. The double-rotating scroll type compressor 1 includes a supercharger that compresses combustion air (fluid) supplied to an internal combustion engine such as a vehicle engine, a compressor for supplying compressed air to an electrode of a fuel cell, and a railway. It can be used as a compressor for supplying compressed air used for a vehicle braking device such as.

The double-rotation scroll type compressor 1 includes a housing 3, a motor (drive unit) 5 housed on one end side of the housing 3, a drive side scroll member 70 housed on the other end side of the housing 3, and a driven side scroll member. It has 90 and.

The housing 3 has a substantially cylindrical shape, and includes a motor accommodating portion 3a for accommodating the motor 5 and a scroll accommodating portion 3b for accommodating the scroll members 70 and 90.
A discharge port 3d for discharging compressed air is formed at the end of the scroll accommodating portion 3b. Although not shown in FIG. 1, the housing 3 is provided with an air suction port for sucking air.

The motor 5 is driven by being supplied with electric power from a power supply source (not shown). The rotation control of the motor 5 is performed by a command from a control unit (not shown). The stator 5a of the motor 5 is fixed to the inner peripheral side of the housing 3. The rotor 5b of the motor 5 rotates around the drive side rotation axis CL1. A drive shaft 6 extending on the drive-side rotation axis CL1 is connected to the rotor 5b. The drive shaft 6 is connected to a drive shaft portion 71d fixed to the first drive side scroll portion 71 of the drive side scroll member 70.

A drive-side bearing 11 that rotatably supports the drive shaft 6 is provided at the front end (left end in FIG. 1) of the drive shaft 6. The rear end of the drive shaft 6 (right end in FIG. 1), that is, the end of the drive shaft 6 on the opposite side of the drive side scroll member 70, rotatably supports the drive shaft 6 with the housing 3. A rear end bearing 17 is provided.

The drive-side scroll member 70 includes a first drive-side scroll portion 71 on the motor 5 side and a second drive-side scroll portion 72 on the discharge port 3d side.
The first drive-side scroll portion 71 includes a first drive-side end plate 71a and a first drive side wall body 71b.
The first drive-side end plate 71a extends in a direction orthogonal to the drive-side rotation axis CL1. A drive shaft portion 71d extending along the drive side rotation axis CL1 is fixed to the rotation center of the first drive side end plate 71a.

A center plate (bearing support member) 20 is fixed to the drive shaft portion 71d. The center plate 20 extends parallel to the first drive side end plate 71a.

The first drive side end plate 71a has a substantially disk shape when viewed in a plan view. As shown in FIG. 2, three first driving side wall bodies 71b having a spiral shape, that is, three rows are provided on the first driving side end plate 71a. The first drive side wall body 71b, which has three articles, is arranged at equal intervals around the drive side rotation axis CL1. The number of rows of the first driving side wall body 71b may be one or two, or may be four or more.

As shown in FIG. 1, the second drive side scroll portion 72 includes a second drive side end plate 72a and a second drive side wall body 72b. The second driving side wall body 72b has three articles like the first driving side wall body 71b (see FIG. 2) described above. The number of rows of the second driving side wall body 72b may be one or two, or may be four or more.

A second drive-side shaft portion 72c extending in the drive-side rotation axis CL1 direction is connected to the second drive-side end plate 72a. The second drive side shaft portion 72c is rotatably provided with respect to the housing 3 via a second drive side bearing 14 which is a ball bearing. A discharge port 72d is formed on the second drive-side end plate 72a along the drive-side rotation axis CL1.

Between the second drive side shaft portion 72c and the housing 3, there are two second drive shaft portions on the tip side (left side in FIG. 1) of the second drive side shaft portion 72c with respect to the second drive side bearing 14. A seal member 26 is provided. The two seal members 26 for the second drive shaft portion and the second drive side bearing 14 are arranged at a predetermined interval in the drive side rotation axis CL1 direction. A lubricant such as grease, which is a semi-solid lubricant, is sealed between the two seal members 26 for the second drive shaft. The number of the second drive shaft portion seal member 26 may be one. In this case, the lubricant is sealed between the second drive shaft portion sealing member 26 and the second drive side bearing 14.

The first drive-side scroll portion 71 and the second drive-side scroll portion 72 are fixed so that the tips (free ends) of the wall bodies 71b and 72b face each other. The first drive-side scroll portion 71 and the second drive-side scroll portion 72 are fixed by bolts 31 fastened to flange portions 73 provided at a plurality of locations in the circumferential direction so as to project outward in the radial direction. ..

In the driven side scroll member 90, the driven side end plate 90a is located substantially at the center in the axial direction (horizontal direction in the drawing). A through hole 90h is formed in the center of the driven side end plate 90a so that the compressed air flows to the discharge port 72d.

The driven side wall bodies 91b and 92b are provided on both sides of the driven side end plate 90a, respectively. The first driven side wall body 91b installed on the motor 5 side from the driven side end plate 90a is meshed with the first driving side wall body 71b of the first driving side scroll portion 71, and is from the driven side end plate 90a to the discharge port 3d side. The installed second driven side wall body 92b is meshed with the second driving side wall body 72b of the second driving side scroll portion 72.

As shown in FIG. 3, the first driven side wall body 91b is provided with three, that is, three articles. The driven side wall bodies 91b having three rows are arranged at equal intervals around the driven side rotation axis CL2. The second driven side wall body 92b has the same configuration. The number of rows of the driven side wall bodies 91b and 92b may be one or two, or may be four or more.

A support member 33 is provided on the discharge port 3d side (left side in FIG. 1) of the driven side scroll member 90. The support member 33 is fixed to the tip (free end) of the second driven side wall body 92b by a bolt 25.

A shaft portion 35a for the support member is provided on the central shaft side of the support member 33, and the shaft portion 35a for the support member is provided with respect to the housing 3 via a bearing 38 for the second support member which is a ball bearing. It is fixed. As a result, the driven side scroll member 90 rotates around the driven side rotation axis CL2 via the support member 33.

A first side plate (bearing support member) 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 to the tip (free end) of the first driven side wall body 91b by bolts 28. At the center of rotation of the first side plate 27, a hole portion 27h for the first side plate is formed so as to penetrate the drive shaft portion 71d.

A second side plate (bearing support member) 30 is provided on the motor 5 side of the first side plate 27 at a predetermined interval. The second side plate 30 is fixed to the first side plate 27 by bolts 34. At the center of rotation of the second side plate 30, a hole 30h for a second side plate is formed so as to penetrate the drive shaft portion 71d.

A shaft portion 30a for the second side plate is provided on the central shaft side of the second side plate 30, and the shaft portion 30a for the second side plate is via a bearing 32 for the second side plate which is a ball bearing. Is fixed to the housing 3. As a result, the driven side scroll member 90 rotates around the driven side rotation axis CL2 via the second side plate 30 and the first side plate 27.

As shown in FIG. 1, a crank pin 15 is provided between the first side plate 27 and the second side plate 30 and the center plate 20. The crank pin 15 has a central cylindrical portion 15a and an eccentric shaft portion 15b having an eccentric axis eccentric with respect to the central axis of the cylindrical portion 15a.
A rolling bearing 16 as a ball bearing is provided on the outer periphery of the cylindrical portion 15a. As a result, the cylindrical portion 15a is made rotatable with respect to the center plate 20. A lubricant such as grease is sealed in the rolling bearing 16.
A rolling bearing 18 and a rolling bearing 19 which are ball bearings are provided at both ends of the eccentric shaft portion 15b, respectively. As a result, the eccentric shaft portion 15b is made rotatable with respect to the first side plate 27 and the second side plate 30. Grease (lubricant) is sealed in each of the eccentric shaft bearings 18 and 19.

The crank pin 15 and the bearings 16, 18 and 19 are used as a synchronous drive mechanism for transmitting a driving force from the drive shaft portion 71d to the driven side scroll member 90 so that both scroll members 70 and 90 revolve and rotate in synchronization. Be done.
A plurality of synchronous drive mechanisms provided with the crankpins 15 are preferably provided, and for example, three synchronous drive mechanisms are provided around the rotation axes CL1 and CL2 at equal angular intervals.

In FIG. 4, the circumference of the eccentric shaft portion 15b of the crank pin 15 is enlarged and shown. A rolling bearing 18 is provided on the eccentric shaft portion 15b. In the following description, the rolling bearing 18 will be used, but the same applies to the rolling bearing 19 and the rolling bearing 16.

The rolling bearing 18 includes an outer ring 18a, an inner ring 18b, balls 18c arranged between the outer ring 18a and the inner ring 18b, and a cage (not shown) for holding each ball 18c at equal intervals. ..
The outer ring 18a is fitted to a circular groove formed in the first side plate. The inner ring 18b is fitted to the eccentric shaft portion 15b.
A lubricant such as grease is sealed between the outer ring 18a and the inner ring 18b.
A sealing member 40 for sealing the lubricant is provided on the side (right side in FIG. 4) of the rolling bearing 18. The seal member 40 has an annular shape, and the outer peripheral side is fixed to the side portion of the outer ring 18a. The seal member 40 is not fixed to the inner ring 18b, and a predetermined gap is provided with respect to the side portion of the inner ring 18b. The inner peripheral end of the seal member 40 extends to the side portion of the inner ring 18b, and more specifically, extends to the inner peripheral side from the outer circumference of the inner ring 18b.

A snap ring 42 for fixing the seal member 40 in a fixed position is provided on the side (right side in the figure) of the seal member 40. The outer circumference of the snap ring 42 is fitted to the snap ring groove 43 formed in the first side plate 27.

The arrow of reference numeral A0 shown in FIG. 4 indicates the direction of the centrifugal force due to the rotation of the first side plate 27, similarly to the reference numeral A0 of FIG.

The double-rotation scroll type compressor 1 having the above configuration operates as follows.
When the drive shaft 6 is rotated around the drive side rotation axis CL1 by the motor 5, the center plate 20 also rotates around the drive side axis CL1 together with the drive side scroll member 70 via the drive shaft portion 71d connected to the drive shaft 6. To do. The driving force transmitted to the center plate 20 by the rotation of 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 synchronous driving mechanism. , The driven side scroll member 90 rotates around the driven side rotation axis CL2. At this time, the crank pins 15 rotate with respect to the center plate 20 and both side plates via the bearings 16, 18 and 19, so that the scroll members 70 and 90 relatively revolve around.

When both scroll members 70 and 90 revolve around, air sucked from the suction port of the housing 3 is sucked from the outer peripheral side of both scroll members 70 and 90, and a compression chamber formed by both scroll members 70 and 90 is formed. Is taken in by. Then, the compression chamber formed by the first driving side wall body 71b and the first driven side wall body 91b and the compression chamber formed by the second driving side wall body 72b and the second driven side wall body 92b are separately compressed. To. The volume of each compression chamber decreases as it moves toward the center, and the air is compressed accordingly. The air compressed by the first driving side wall body 71b and the first driven side wall body 91b passes through the through hole 90h formed in the driven side end plate 90a, and passes through the second driving side wall body 72b and the second driven side wall body 92b. The air is merged with the air compressed by the above, and the merged air passes through the discharge port 72d and is discharged to the outside from the discharge port 3d of the housing 3.

According to this embodiment, the following effects are exhibited.
As described with reference to FIG. 4, since the outer ring 18a of the rolling bearing 18 is fitted to the first side plate 27, it rotates together with the first side plate 27 and revolves around the driven side rotation axis CL2. Since the seal member 40 is fixed to the outer ring 18a, it revolves around the driven side rotation axis CL2 in the same manner as the outer ring 18a. On the other hand, the inner ring 18b not only revolves together with the outer ring 18a, but also rotates around the central axis of the eccentric shaft portion 15b together with the eccentric shaft portion 15b because it is fitted to the eccentric shaft portion 15b of the crankpin 15. As a result, as described with reference to FIG. 13, the lubricant attracted to the inner peripheral side of the outer ring 18a due to the centrifugal force due to the revolutionary motion moves from the outer peripheral side of the inner ring 18b to the outside of the rolling bearing 18 due to the rotation of the inner ring 18b. There is a risk of leakage. On the other hand, since the seal member 40 extends to the side portion of the inner ring 18b, it is possible to prevent the lubricant from leaking from the inner ring 18b side to the outside of the rolling bearing 18. As a result, it is possible to prevent poor lubrication due to leakage of lubricating oil and extend the life of the synchronous drive mechanism.

[Modification 1]
The present embodiment can be modified as follows.
As shown in FIG. 5, a C chamfer 40a is formed on the inner peripheral edge of the seal member 40 at a position facing the side portion of the inner ring 18b. The C chamfer 40a is an inclined surface in which the distance from the side portion of the inner ring 18b increases toward the inner peripheral side of the seal member 40. The C chamfered shape is formed over the entire circumference of the inner peripheral edge of the seal member 40. The inclined surface may have another shape such as an R surface instead of the C chamfer 40a.

According to the first modification, even if the lubricant leaks from the inner peripheral side of the seal member 40, the distance from the side portion of the inner ring 18b increases toward the inner peripheral side of the seal member 40. Since 40a is formed, as shown by the arrow indicated by reference numeral A5 in FIG. 5, the lubricant leaked through the crank pin 15 is positioned in the centrifugal direction by the centrifugal force of the revolving motion due to the rotation of the first side plate 27. It can be effectively received by the C chamfer 40a. As a result, the depletion of the lubricant in the rolling bearing 18 can be prevented, and the life of the synchronous drive mechanism can be extended.

[Modification 2]
The above-mentioned modification 1 can be further modified as follows.
As shown in FIG. 6, the C chamfer 40a is formed only on the outer peripheral side of the revolving motion of the rolling bearing 18 in the inner peripheral edge of the seal member 40. Therefore, the C chamfer 40a is not formed on the inner peripheral side of the revolving motion of the rolling bearing 18, and the corner portion 40b is left. The range in which the C chamfer 40a is provided is, for example, 90 °, that is, 180 ° on both sides of the direction of centrifugal force due to the revolutionary motion of the rolling bearing 18 (specifically, the outer side in the radial direction about the driven side rotation axis CL2). It is a range.

By forming the C chamfer 40a formed on the inner peripheral edge of the seal member 40 only on the outer peripheral side of the rolling bearing 18's revolving motion, the lubricant leaked by the centrifugal force due to the revolving motion of the rolling bearing 18 is formed on the outer peripheral side. It can be received by the C chamfer 40a formed in. On the other hand, since the rolling bearing 18 is not provided with an inclined surface on the inner peripheral side of the revolving motion and has a corner portion 40b, leakage of the lubricant can be prevented as much as possible.

[Modification 3]
The present embodiment can be modified as follows.
FIG. 7 shows the leakage path of the lubricant indicated by the arrow of reference numeral A6 for the same configuration as in FIG. As described with reference to FIG. 4, it is preferable that the lubricant G flows in the direction of the arrow A5 due to the centrifugal force due to the revolving motion, but the lubricant flows in the axial direction of the eccentric shaft portion 15b as shown by the arrow A6. A case is also assumed. In such a case, the lubricant cannot be recovered by the rolling bearing 18, which may result in poor lubrication.

On the other hand, in this modification, the shape of the eccentric shaft portion 15b is changed as shown in FIG. Specifically, the first shaft portion 15b1 of the eccentric shaft portion 15b to which the inner ring 18b is fitted is connected to the first shaft portion 15b1 and has a diameter larger than that of the first shaft portion 15b1. A shaft portion 15b2 is provided. As a result, a stepped portion 15b3 for partitioning the first shaft portion 15b1 and the second shaft portion 15b2 is formed. It is preferable that the step portion 15b3 is provided at a position facing the inner peripheral end of the seal member 40. However, it may be provided at a position farther when viewed from the side of the inner ring 18b from the position opposed to the inner peripheral end of the seal member 40 (the right in the drawing).

By providing the stepped portion 15b3 in this way, the lubricant leaked from the rolling bearing 18 is guided to the first shaft portion 15b1 having a diameter smaller than that of the second shaft portion 15b2, and the lubricant is lubricated from between the seal member 40 and the inner ring 18b. Can accept oil.

[Second Embodiment]
Next, the second embodiment of the present invention will be described. In this embodiment, the fixing position of the seal member is different from that in the first embodiment. Since other points are the same as those in the first embodiment, the description thereof will be omitted.
As shown in FIG. 9, the seal member 44 is fixed to the side portion of the inner ring 18b of the rolling bearing 18, and is not fixed to the outer ring 18a. The outer peripheral end of the seal member 44 extends to the side portion of the outer ring 18a.
On the side of the seal member 44, a side wall portion 27s connected to the first side plate 27 and provided so as to surround the outer peripheral side of the seal member 44 is provided. The side wall portion 27s extends toward the eccentric shaft portion 15b and has a substantially disk shape. A predetermined gap is provided between the inner peripheral end of the side wall portion 27s and the eccentric shaft portion 15b.

According to this embodiment, the following effects are exhibited.
Since the outer ring 18a of the rolling bearing 18 is fitted to the first side plate 27, it rotates together with the first side plate 27 and revolves around the driven side rotation axis CL2. On the other hand, the inner ring 18b not only revolves together with the outer ring 18a, but also rotates around the central axis of the eccentric shaft portion 15b together with the eccentric shaft portion 15b because it is fitted to the eccentric shaft portion 15b. As a result, the lubricant attracted to the inner peripheral side of the outer ring 18a due to the centrifugal force due to the revolution movement may leak from the outer peripheral side of the inner ring 18b to the outside of the rolling bearing 18 due to the rotation of the inner ring 18b. On the other hand, since the seal member 44 is fixed to the side portion of the inner ring 18b and extends to the side portion of the outer ring 18a, the lubricant G leaks from the inner ring 18b side to the outside of the rolling bearing 18. It can be suppressed.

A side wall portion 27s is provided on the side of the seal member 44 so as to surround the outer peripheral side of the seal member 44. As a result, the lubricant G leaked to the outer peripheral side of the rolling bearing 18 due to the centrifugal force of the revolving motion can be retained. Further, the inner ring 18b rotates around the central axis of the eccentric shaft portion 15b due to rotation, so that the lubricant G tends to leak from the outer peripheral side of the seal member 44. However, the frictional force between the seal member 44 and the side wall portion 27s with respect to the lubricant G scrapes out the lubricant G by a ball 18c or a cage (not shown) provided between the inner ring 18b and the outer ring 18a. Since it is smaller than the frictional force to be applied, the amount of the lubricant G leaking from the outer peripheral side of the seal member 44 through the space S1 between the side wall portion 27s is small.

[Third Embodiment]
Next, a third embodiment of the present invention will be described. The present embodiment is different from the first embodiment in that the tip seal 45 is provided between the first side plate 27 and the center plate 20. Therefore, the description of the configuration similar to that of the first embodiment will be omitted.

As shown in FIG. 10, an annular tip seal 45 is fitted in the groove formed in the first side plate 27. The chip seal 45 is made of resin, for example. The tip of the tip seal 45 (right end in FIG. 10) is in contact with the end face of the center plate 20. The diameter of the chip seal 45 is larger than that of the rolling bearing 18. On the inner peripheral side of the chip seal 45, the leakage path of the lubricant from the rolling bearing 18 and the rolling bearing 16 is blocked.

According to this embodiment, the following effects are exhibited.
Since the chip seal 45 that seals the space between the rolling bearing 18 side and the rolling bearing 16 side is provided, the lubricant leaking from the rolling bearing 18 and the rolling bearing 16 can be sealed. Further, since the lubricant can be sealed on the rolling bearing 18 side and the rolling bearing 16 side, it is possible to prevent the fluid before and after compression from being contaminated with the lubricant.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described. In this embodiment, the installation direction of the snap ring 42 is different from that in the first embodiment. Therefore, the description of the configuration similar to that of the first embodiment will be omitted.

As shown in FIG. 11, the snap ring 42 has a substantially C shape having one open portion 42a. Retaining rings 42b for inserting a mounting jig are provided at each end facing each other at the opening portion 42a. A jig is inserted into the retaining ring 42b, elastically deformed so as to reduce the diameter of the snap ring 42, and fitted into the snap ring groove 43 (see FIG. 4).
In the snap ring 42, the opening portion 42a is arranged so as to face the driven side rotation axis CL2, which is the center of rotation.

According to this embodiment, the following effects are exhibited.
Since the snap ring 42 has the open portion 42a, the weight of the open portion 42a side is relatively light, and the weight of the opposite side of the open portion 42a is heavy. Therefore, when a centrifugal force around the driven side rotation axis CL2 due to the revolution motion is applied to the snap ring 42, the opposite side of the opening portion 42a tends to move in the centrifugal force direction. In consideration of this, the open portion 42a of the snap ring 42 is oriented toward the driven side rotation axis CL2, which is the rotation center of the first side plate 27. As a result, it is possible to prevent the snap ring 42 from rotating due to centrifugal force and the seal member 40 from shifting and sliding, and the seal member 40 can be securely fixed.

[Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described. In this embodiment, the shape of the second side plate 30 for fixing the rolling bearing 19 is different from that in the first embodiment. Therefore, the description of the configuration similar to that of the first embodiment will be omitted.

FIG. 12 shows the circumference of the rolling bearing 19 provided on the second side plate 30. A sealing wall portion 30w of the second side plate 30 is provided on the side portion (left side in the drawing) of the rolling bearing 19 so as to seal the rolling bearing 19 from the side. The sealing wall portion 30w is provided with a recess 30r formed in an annular shape from the outer ring 19a toward the side and corresponding to the outer ring 19a.
On the inner peripheral side of the recess 30r, a protruding portion 30e protruding toward the rolling bearing 19 side is provided, and on the inner peripheral side of the protruding portion 30e, the protrusion 30e is opened toward the inner peripheral side at a position corresponding to the inner ring 19b. An opening 30f is provided.

According to this embodiment, the following effects are exhibited.
A recess 30r is provided in the sealing wall portion 30w, and the recess 30r is used as an oil pocket of the lubricant G to temporarily hold the lubricant leaked from the rolling bearing 19. As a result, even if the lubricant leaks from the recess 30r located above when stopped, it is possible to avoid insufficient lubrication by collecting the lubricant at the recess 30r located below as shown by arrow A5. ..
The configuration of this embodiment can also be applied to the first side plate 27 that accommodates the rolling bearing 18.

1 Double-rotation scroll type compressor 3 Housing 3a Motor housing 3b Scroll housing 3d Discharge port 5 Motor (drive)
5a Stator 5b Rotor 6 Drive shaft 11 Drive side bearing 15 Crank pin (synchronous drive mechanism)
15a Cylindrical part 15b Eccentric shaft part 15b1 First shaft part 15b2 Second shaft part 15b3 Step part 16 Rolling bearing 17 Rear end bearing 18 Rolling bearing 18a Outer ring 18b Inner ring 18c Ball 19 Rolling bearing 20 Center plate 25 Bolt 26 Second drive shaft part Seal member 27 1st side plate 27b 1st protruding wall part 27h 1st side plate hole part 27s Side wall part 28 Bolt 30 2nd side plate 30a 2nd side plate shaft part 30b 2nd protruding wall part 30e Protruding part 30f Opening 30h Hole for 2nd side plate 30r Recess 30w Sealing wall 31 Bolt 32 Bearing for 2nd side plate 33 Support member 40 Sealing member 40a C Chamfering (inclined surface)
40b Square 42 Snap ring 42a Open 42b Stop ring 43 Snap ring groove 44 Seal member 45 Chip seal 70 Drive side scroll member 71 1st drive side scroll member 71a 1st drive side end plate 71b 1st drive side wall body 71d Drive Shaft 72 2nd drive side scroll 72a 2nd drive end plate 72b 2nd drive side wall 72c 2nd drive side shaft 72d Discharge port 73 Flange 90 Drive side scroll member 90h Through hole 91b 1st drive side wall 92b 2nd driven side wall 100 Bearing support member 102 Ball bearing 102a Outer ring 102b Inner ring 104 (of crank pin) Shaft A0 Direction of centrifugal force due to revolution CL1 Drive side rotation axis CL2 Driven side rotation axis G Lubricant O1 Rotation center O2 (crank) Rotation center S space (of the pin shaft)

Claims (9)

A drive-side scroll member having a spiral drive side wall body that is rotationally driven around the rotation axis by the drive unit and is arranged on the drive-side end plate.
A spiral driven side wall body corresponding to the driving side wall body is arranged on the driven side end plate, and the driven side wall body is meshed with the driving side wall body to form a compression space with the driven side scroll member. ,
A synchronous drive mechanism that transmits a driving force from the drive-side scroll member to the driven-side scroll member so that the drive-side scroll member and the driven-side scroll member rotate in the same direction at the same angular velocity.
With
The synchronous drive mechanism includes a crank pin and a rolling bearing that rotatably supports a shaft portion of the crank pin.
The rolling bearing includes an inner ring fitted to the shaft portion and an outer ring fitted to a bearing support member that supports the shaft portion.
A seal member extending to the side of the inner ring is fixed to the side of the outer ring.
A double-rotation scroll type compressor characterized in that a predetermined gap is provided between the inner peripheral end of the seal member and the side portion of the inner ring. The sealing member is characterized in that an inclined surface is formed on the inner peripheral edge of the inner ring facing the side portion so that the distance from the side portion of the inner ring increases toward the inner peripheral side of the sealing member. The double rotation scroll type compressor according to 1. The double-rotation scroll type compressor according to claim 2, wherein the inclined surface is formed only on the outer peripheral side of the revolving motion of the rolling bearing among the inner peripheral edges of the sealing member. The crank pin includes a first shaft portion to which the inner ring is fitted, and a second shaft portion connected to the first shaft portion and having a diameter larger than that of the first shaft portion.
The step portion that separates the first shaft portion and the second shaft portion is farther from the side portion of the inner ring than the position facing the inner peripheral end of the seal member or the position facing the inner peripheral end. The double-rotation scroll type compressor according to any one of claims 1 to 3, wherein the compressor is provided at a position. A drive-side scroll member having a spiral drive side wall body that is rotationally driven around the rotation axis by the drive unit and is arranged on the drive-side end plate.
A spiral driven side wall body corresponding to the driving side wall body is arranged on the driven side end plate, and the driven side wall body is meshed with the driving side wall body to form a compression space with the driven side scroll member. ,
A synchronous drive mechanism that transmits a driving force from the drive-side scroll member to the driven-side scroll member so that the drive-side scroll member and the driven-side scroll member rotate in the same direction at the same angular velocity.
With
The synchronous drive mechanism includes a crank pin and a rolling bearing that rotatably supports a shaft portion of the crank pin.
The rolling bearing includes an inner ring fitted to the shaft portion and an outer ring fitted to a bearing support member that supports the shaft portion.
A seal member extending to the side of the outer ring is fixed to the side of the inner ring.
A double-rotation scroll type compressor characterized in that a predetermined gap is provided between the outer peripheral end of the seal member and the side portion of the outer ring. The double rotation according to claim 5, wherein a side wall portion connected to the bearing support member and provided so as to surround the outer peripheral side of the seal member is provided on the side of the seal member. Scroll type compressor. A drive-side scroll member having a spiral drive side wall body that is rotationally driven around the rotation axis by the drive unit and is arranged on the drive-side end plate.
A spiral driven side wall body corresponding to the driving side wall body is arranged on the driven side end plate, and the driven side wall body is meshed with the driving side wall body to form a compression space with the driven side scroll member. ,
A synchronous drive mechanism that transmits a driving force from the drive-side scroll member to the driven-side scroll member so that the drive-side scroll member and the driven-side scroll member rotate in the same direction at the same angular velocity.
With
The synchronous drive mechanism includes a crank pin and a rolling bearing that rotatably supports a shaft portion of the crank pin.
The rolling bearing includes an inner ring fitted to the shaft portion and an outer ring fitted to a bearing support member that supports the shaft portion.
A tip seal is provided which is arranged on the outer peripheral side of the rolling bearing with respect to the central axis of the shaft portion of the crank pin and seals the space on the rolling bearing side between the bearing support member and the wall portion facing the rolling bearing. A double-rotating scroll type compressor characterized by bearings. A snap ring provided on the side of the sealing member and fixing the sealing member is provided.
The snap ring has a substantially C shape having one open portion and has a substantially C shape.
The double-rotation scroll type compressor according to any one of claims 1 to 6, wherein the open portion is arranged so as to face the rotation center of the bearing support member. A drive-side scroll member having a spiral drive side wall body that is rotationally driven around the rotation axis by the drive unit and is arranged on the drive-side end plate.
A spiral driven side wall body corresponding to the driving side wall body is arranged on the driven side end plate, and the driven side wall body is meshed with the driving side wall body to form a compression space with the driven side scroll member. ,
A synchronous drive mechanism that transmits a driving force from the drive-side scroll member to the driven-side scroll member so that the drive-side scroll member and the driven-side scroll member rotate in the same direction at the same angular velocity.
With
The synchronous drive mechanism includes a crank pin and a rolling bearing that rotatably supports a shaft portion of the crank pin.
The rolling bearing includes an inner ring fitted to the shaft portion and an outer ring fitted to a bearing support member that supports the shaft portion.
A sealing wall portion fixed to the bearing support member and sealing the rolling bearing from the side is provided on the side portion of the rolling bearing.
The sealing wall portion is provided with a recess formed laterally from the outer ring and formed in an annular shape so as to correspond to the outer ring. Machine.

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