JP2003322149A - Eccentric thrust bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To stabilize the action of a ball unit, and to increase a life span, in an eccentric thrust bearing using the ball unit for increasing a load capacity and improving action smoothness. <P>SOLUTION: The layout relation of moving pins 30, 31 of a moving race 11 and fixed pins 40, 41 of a fixed race 12 to through holes 22, 23 formed in on a cage ring 14 of the ball unit 13 equipped to the eccentric thrust bearing 10, is specified. Therefore, the cage ring 14 is made to follow the moving race 11 with eccentric turning and the rotating of the moving race 11, and the action of the cage ring 14 is regulated in a diameter direction without backlash. Therefore, a ball 15 of the ball unit 13 is stabilized in action and hard to slip. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an eccentric thrust bearing which supports an eccentric turning motion in a scroll compressor or the like.

[0002]

2. Description of the Related Art In a conventional scroll compressor, an orbiting scroll member which makes an eccentric orbiting motion with respect to a frame is supported by an eccentric thrust bearing.

An eccentric thrust bearing of this type is disclosed in, for example, Japanese Patent Application Laid-Open Nos. 11-93950 and 10-184676.
As shown in Japanese Patent Laid-Open Publication No. 2004-242, one rolling element is installed in a circular raceway groove provided at several circumferential positions on each inner surface of a pair of two races.
It is arranged so that they can be rotated and rotated one by one.

In the former publication, balls are used as rolling elements, and in the latter publication, so-called double tapered rollers such as abacus balls are used as rolling elements.

In the conventional example using the above balls, although the smoothness is excellent, the number of balls used is limited,
There is a limit to increasing the load capacity. On the other hand, in the conventional example using both of the above tapered rollers, although it is possible to cope with an increase in load capacity, the smoothness of the operation of the orbiting scroll member is deteriorated because there are many sliding portions between the both tapered rollers and the circular raceway groove. Is pointed out.

On the other hand, the applicant of the present application has proposed a structure as shown in Japanese Unexamined Patent Publication No. 2001-74043 as a structure that achieves both an increase in load capacity and an improvement in smoothness of operation. In this application, a cage ring is inserted between a pair of races, and a plurality of balls are inserted into fan-shaped windows provided at several places on the circumference of the cage ring. In order to restrict the movement of the cage ring, at least two pins are provided in one race and at least two through holes are provided in the cage ring, and the diameter of the through hole is set to be larger than that of the pins. The pin is inserted into the through hole.

[0007]

In the above-mentioned conventional example, since the pin is inserted into the through hole with a predetermined play, the retainer ring has the pin and the radial direction with respect to the one race. It is in a state that it has "rattle" that can freely move in all directions of 360 degrees. Therefore, the eccentric turning trajectory of the cage ring is likely to be irregular, and unnecessary force is applied to the ball to make it easier to slip. There is room for improvement here.

[0008]

The eccentric thrust bearing of the present invention is interposed between a movable member which makes an eccentric swivel motion and a fixed member which is arranged to face the movable member in the axial direction, It has a ball unit that is eccentrically rotatable between both members. This ball unit has a cage ring having a fan-shaped window penetrating in the axial direction except at least two locations on the circumference, and a large number of balls rotatably housed and retained in each sector-shaped window of the cage ring. including. At least one circular recess is provided on each of the surfaces of the cage ring that face the movable member and the fixed member. A pin that is inserted into the first circular recess is provided at a portion of the surface of the movable member that faces the retainer ring and that corresponds to the first circular recess, and the holding member is provided with the pin. A pin to be inserted into the second circular recess is provided at a portion of the surface facing the container ring corresponding to the second circular recess. The pins on the movable member side and the pins on the fixed member side are abutted against the inner peripheral wall surfaces of the corresponding circular recesses in a state in which they are offset from a predetermined phase position on the circumference of the corresponding circular recesses. ing. The arrangement relationship between the pin on the movable member side and the pin on the fixed member side is set to be 180 degrees opposite to each other assuming an imaginary situation in which the circular concave portions are concentrically overlapped and arranged.

As described above, since a ball unit such as a so-called full ball bearing is used to roll the ball group with respect to the movable member and the fixed member, the load capacity is increased and the operation is smoothed. And wear resistance are improved. In this configuration, by the circular recess and the pin,
The eccentric turning range of the cage ring of the ball unit is restricted by both the movable member and the fixed member. Moreover, by specifying the positional relationship between the pin on the movable member side and the pin on the fixed member side with respect to the circular concave portion, the cage ring can be made to follow the movable member along with the eccentric turning motion of the movable member, and The movement is restricted in all directions in the radial direction. As a result, the behavior of the ball in the ball unit is stable and less likely to slip.

The eccentric thrust bearing of the present invention is interposed between a movable member which makes an eccentric turning motion and a fixed member which is arranged so as to oppose the movable member in the axial direction, and is eccentrically rotatable between both members. It has a ball unit inserted in the.
The ball unit includes a cage ring having a fan-shaped window penetrating in the axial direction except at least two places on the circumference,
The cage ring includes a plurality of balls rotatably housed and retained in each fan-shaped window. A plurality of circular recesses are provided on each of the surfaces of the cage ring that face the movable member and the fixed member. Pins to be inserted into the respective circular recesses are provided at portions of the surfaces of the movable member and the fixed member facing the retainer ring corresponding to the circular recesses. Each pin on the movable member side is in contact with the inner peripheral wall surface of the corresponding circular recess in a state in which the pins are arranged offset to the same phase position on the circumference of each circular recess, and The pins on the side of the fixing member are in contact with the inner peripheral wall surfaces of the corresponding circular recesses in a state in which the pins are arranged at the same phase position on the circumference of the circular recesses, offset from each other. The positional relationship between the pins on the movable member side and the pins on the fixed member side is set to be 180 degrees opposite to each other assuming an imaginary situation in which the circular concave portions are concentrically overlapped and arranged.

In this case, the movable member side and the fixed member side are provided with pins to be inserted into the respective circular recesses of the cage ring, so that the behavior of the cage ring is further restricted by the pins. improves.

The eccentric thrust bearing further has a movable race fixed to the movable member and a fixed race fixed to the fixed member, and the ball unit is eccentrically rotatable between these races. Can be inserted. In this case, the facing surfaces of the movable member and the fixed member are not used for bearing raceway to increase the strength. The pins are provided on both races. In this case, it is not necessary to provide a pin for a movable member or a fixed member that is a member other than the bearing.

Further, the plurality of circular recesses may be arranged at equal intervals on the circumference of the cage ring. In this case, since the balls can be arranged in a well-balanced manner, the amount of displacement of the ball unit in all radial directions of the fixed member and the fixed race can be made substantially equal.

[0014]

1 to 6 show an embodiment of the present invention. In the figure, 1 is a scroll compressor.

This scroll compressor 1 has a generally well-known structure. For example, a rotating shaft 2 such as a motor shaft is driven to rotate, and an orbiting scroll member 3 connected to an eccentric shaft portion 2a at the shaft end thereof. The eccentric orbiting motion of the fluid changes the volume of the compression chamber between the orbiting scroll member 3 and the fixed scroll member 4 to compress the fluid in the compression chamber.

The rotary shaft 2 is 2 with respect to the frame 5.
It is supported via two radial type rolling bearings 6 and 7. Further, the eccentric shaft portion 2a of the rotary shaft 2 is fitted and attached to the cylindrical boss portion 3a of the orbiting scroll member 3 via a radial type rolling bearing 8. Further, between the orbiting scroll member 3 and the frame 5, an eccentric thrust bearing 10 for supporting the eccentric orbiting motion of the orbiting scroll member 3 is arranged.

The eccentric thrust bearing 10 is provided with upper and lower two races 11 and 12, and a ball unit 13 interposed between the pair of races 11 and 12.

The upper race 11 is fixedly attached to the lower surface of the orbiting scroll member 3. The lower race 12 is fixedly attached to the upper surface of the frame 5. Due to this relationship, the upper race 11
Since the eccentric orbiting motion is performed integrally with the orbiting scroll member 3,
Below, it is called a movable race, and the lower race 12 is
Since it is fixed to the frame 5 and is immobile, it will be referred to as a fixed race hereinafter. In order to fix both races 11 and 12 to the orbiting scroll member 3 and the frame 5, although not shown, for example, uneven portions may be separately provided on both and the fitting may be performed by fitting them together. it can.

The ball unit 13 includes a cage ring 14
In this configuration, a large number of balls 15 are held. The cage ring 14 is provided with fan-shaped windows 16a and 16b which penetrate the cage ring 14 in the axial direction except at two locations on the circumference, which are opposed to each other by 180 degrees. The group of balls 15 is housed and held in the respective fan-shaped windows 16a and 16b of the cage ring 14 so as to be rotatable and adjacent to each other in the circumferential direction.

Incidentally, the fan-shaped window 16a of the cage ring 14,
Grooves 18 and 19 are provided on the outer circumference of the inner diameter side annular portion and the inner circumference of the outer diameter side annular portion which form 16b. When each ball 15 is axially hooked to the ring-shaped projections on both sides of the grooves 18 and 19, each fan-shaped window 1
Each ball 15 is held in a non-separable state in 6a and 16b in a rotatable state. The group of balls 15 is forcibly fitted and attached to the sector windows 16a and 16b of the cage ring 14 by a snap fit from the axial direction.

The axial dimension of the cage ring 14 is
As shown in FIG. 4, it is set to be slightly smaller than the diameter dimension of the ball 15. As a result, only the group of balls 15 contacts the two races 11 and 12, and the cage ring 14 does not contact the two races 11 and 12.

By the way, the races 11 and 12 described above
Is formed by a metal material such as JIS standard SUJ2 or SAE standard 5120 that has been subjected to quenching / tempering treatment (substantial quenching) or carburizing / hardening treatment as required, or ceramics.

The cage ring 14 of the ball unit 13 is made of various synthetic resin materials or metal materials. The balls 15 of the ball unit 13 are formed of a general metal material such as bearing steel or ceramics.

As the above ceramic material, for example, silicon nitride is mainly used, and yttria and alumina are used as a sintering aid. In addition, aluminum nitride, titanium oxide, and spinel are appropriately used, as well as alumina and silicon carbide.
Examples include zirconia and aluminum nitride. Specifically, yttria is 1.5 to 5.5% by weight, aluminum nitride is 1 to 2% by weight, alumina is 2 to 4.5% by weight, and titanium oxide is 0.5 to 1.0% by weight, It is preferable to use ceramics with the rest being silicon nitride.

In this embodiment, since the guide form of the cage ring 14 of the eccentric thrust bearing 10 is devised, it will be described below.

First, circular through holes 22 and 23 are formed as circular recesses in the two connecting portions 20 and 20 of the cage ring 14 which are opposed to each other by 180 degrees.

Then, in the movable race 11, the through holes 2 are formed at the portions corresponding to the above two through holes 22 and 23.
Round bar-shaped pins 3 inserted one by one for 2 and 23
0 and 31 are provided. Further, in the fixed race 12 at the portions corresponding to the above two through holes 22 and 23,
Round rod-shaped pins 40 and 41 that are inserted into the through holes 22 and 23 one by one are provided. The pins 30 and 31 on the movable race 11 side are called movable pins, and the pins 40 and 41 on the fixed race 12 side are called fixed pins.

Here, the positional relationship of the movable pins 30 and 31 and the fixed pins 40 and 41 with respect to the two through holes 22 and 23 will be described.

First, as shown in FIG. 3, the first through hole 2
2 is at the 3 o'clock position on the cage ring 14,
Further, the second through hole 23 is arranged at the 9 o'clock position of the timepiece in the cage ring 14.

When the two races 11 and 12 are not attached to the orbiting scroll member 3 and the frame 5, the centers O1 and O2 of both races 11 and 12 and the center O3 of the cage ring 14 are concentric with each other. , The first through hole 22, the first movable pin 30, and the first fixed pin 40 are concentric with each other, and the second through hole 23 and the second
The movable pin 31 and the second fixed pin 41 are concentric with each other.

Moreover, as shown in FIG. 4, the two races 11, 1 are attached to the orbiting scroll member 3 and the frame 5.
When 2 is attached, the movable race 11 is displaced with respect to the fixed race 12 in the 9 o'clock direction of the timepiece, and the movable pins 30 and 31 are set at 9 o'clock of the timepiece on the circumference of the through holes 22 and 23. Position, and the fixing pins 40, 41 are respectively arranged at the position of 3 o'clock of the timepiece, and all the pins 30, 31, 40, 41 are respectively against the inner peripheral wall surfaces of the through holes 22, 23. It will be in abutted state.

From the above, the movable pins 30, 31
Since the fixing pins 40 and 41 abut on the inner peripheral wall surfaces of the through holes 22 and 23 of the cage ring 14 in a state of being stretched 180 degrees diametrically opposite to each other, the respective pins are attached to the through holes 22 and 23. 30, 31, 40, 41 will not rattle.

Here, each of the pins 30, 31, 40, 4 described above
The diameter of 1 is 1/2 of the diameter of the through holes 22 and 23.
Set to less than. In addition, each pin 30, 31, 40, 4
The length of 1 is set to less than 1/2 of the depth of the through holes 22 and 23. Thereby, each pin 30, 31, 40, 41
Will not interfere with each other. Moreover, the distance between the centers of the movable pins 30 and 31 and the centers of the fixed pins 40 and 41 is set to be the same as the distance between the center of the rotary shaft 2 and the center of the eccentric shaft portion 2a. To be done.

Next, the operation will be described. First, as the rotating shaft 2 rotates, the orbiting scroll member 3 and the movable race 1
1 indicates the center O1 as shown in FIGS.
Is rotated around the center O2 of the fixed race 12 in a clockwise direction with eccentricity with time.

As the movable race 11 makes an eccentric turn, the ball unit 13 makes an eccentric turn following the eccentric turn. That is, when the movable race 11 starts to eccentrically rotate, the movable pins 30 and 31 move to the cage ring 14.
The inner peripheral wall surfaces of the through holes 22 and 23 are pulled in the turning direction. As a result, the cage ring 14 rotates eccentrically. At this time, the through holes 22, 23 of the cage ring 14
Movable pins 30, 31 and fixed pin 4 with respect to the inner peripheral wall surface of
The contact position with 0 and 41 is gradually displaced, and the sliding guide is performed.

Moreover, the movable pin 3 of the movable race 11 is
Both 0 and 31 and the fixing pins 40 and 41 of the fixed race 12 are through holes 2 of the cage ring 14 of the ball unit 13.
In the inner circumference of 2, 23, it is always in a state of being stretched in 180 degrees diametrically opposite directions. Therefore, the retainer ring 14 follows the movable race 11 without backlash, so that the retainer ring 14 turns eccentrically while drawing a certain regular trajectory, and the behavior of the ball 15 slides stably. It gets harder. As a result, the orbiting scroll member 3 and the movable race 11 are guided by the rolling action of the large number of balls 15, so that the eccentric orbiting motion of the orbiting scroll member 3 becomes smooth.

As described above, in the eccentric thrust bearing 10 of the present embodiment, a large number of balls 15 are held in a state where they are continuously adjacent to the fan-shaped windows 16a and 16b of the cage ring 14 in the circumferential direction. By setting it to
Since we use as many balls 15 as possible,
The load capacity can be increased according to the number of balls 15 used.

Further, since the group of balls 15 held by the retainer ring 14 is brought into rolling contact with the races 11 and 12, the rotational resistance of the orbiting scroll member 3 can be reduced, and poor. Even when used in harsh environments such as lubrication conditions, smoothness of operation and wear resistance can be improved.

In such a structure, the fixed race 12
The eccentric turning locus of the cage ring 14 is regularly arranged because the ball unit 13 is caused to eccentrically turn without following the movable race 11 as the movable race 11 turns eccentrically with respect to the center of. As a result, the behavior of the ball 14 becomes stable and becomes difficult to slip. Therefore,
Since the operation of the movable race 11 can be stabilized, the life of the bearing can be greatly improved.

The present invention is not limited to the above embodiment, and various applications and modifications are possible.

(1) The number of the through holes may be any number such as three, four ... For example, the case where the number of through holes is four is shown in FIGS. 7 and 8. That is, the retainer ring 14 of the ball unit 13 has four fan-shaped windows 16 a to 1 a.
6d are provided at equal intervals on the circumference, and connecting portions 20 ... Are provided at four positions on the circumference at every 90 degrees. Circular through holes 22 to 25 are provided for each of the four connecting portions 20. In addition, movable race 1
1, the movable pins 30 to 33 are provided at the portions corresponding to the four through holes 22 to 25, respectively. Further, in the fixed race 12, the four through holes 22 to
Fixing pins 40 to 43 are provided one by one in a portion corresponding to 25.

Also in this case, the positional relationship between the movable pins 30 to 33 and the fixed pins 40 to 43 in the through holes 22 to 25 is basically the same as that in the above embodiment.

Further, FIG. 9 shows a case where there are three through holes, for example. That is, the cage ring 14 of the ball unit 13 is provided with three fan-shaped windows 16a to 16c at equal intervals on the circumference, and three fan-shaped windows 16a to 16c are provided at intervals of 120 degrees on the circumference.
Connection parts 20 ... Are provided at various places. Circular through holes 22 to 24 are provided for each of the three connecting portions 20. In the movable race 11, the above 3
The movable pins 30 to 32 are provided one by one at the portions corresponding to the two through holes 22 to 24, respectively. In addition, fixed race 1
2, the fixing pins 40 to 42 are provided one by one at the portions corresponding to the three through holes 22 to 24.

Also in this case, the positional relationship between the movable pins 30 to 32 and the fixed pins 40 to 42 in the through holes 22 to 24 is basically the same as that of the above embodiment.

Thus, the connecting portion 2 of the cage ring 14 is
If the number of 0 ... Is increased to three or four, the strength of the cage ring 14 is improved, and it is advantageous in maintaining the eccentric turning operation of the ball unit 13 more stable.

(2) In the above embodiment, the cage ring 1
One movable pin and one fixed pin are inserted into each of the four through holes. However, for example, as shown in FIG.
When the second and second holes 23 are provided, only one movable pin 30 may be inserted into one through hole 22 and only one fixed pin 40 may be inserted into the other through hole 23. Further, as shown in FIG. 11, when the cage 14 is provided with four through holes 22 to 25, any two through holes 2 are provided.
It is also possible to insert only the movable pins 30 and 31 into the two and 23, respectively, and insert the fixed pins 40 and 41 into the remaining two through holes 24 and 25, respectively.

In this case, the positional relationship between the movable pins 30 and 31 and the fixed pins 40 and 41 is basically the same as that in the above embodiment.

(3) Through hole (2) of the cage ring 14
2 to 25) may be provided with a partition wall at the center of the penetrating direction of the through hole instead of the hole penetrating in the plate thickness direction of the cage ring 14. That is, as shown in FIG. 12, the circular recesses 2 are formed on the upper and lower surfaces of the cage ring 14, respectively.
2a (23a to 25a) and 22b (23b to 25b) may be provided.

(4) The through hole or the circular recess of the cage ring 14 is not provided in the connecting portion 20, but is provided at any place on the surface of the cage ring 14 that faces the movable race 11 and the fixed race 12. be able to.

(5) Through hole (2) of the cage ring 14
2 to 25), the movable pin (30 to 33), and the fixed pin (40 to 43) and / or the outer peripheral surface of the fixed pin (40 to 43) are coated with a suitable solid lubricant, or a special surface treatment is applied. If so, excellent smoothness of operation and wear resistance can be exhibited even when used in a severe environment such as poor lubrication conditions.

Examples of the above-mentioned solid lubricant include soft metals such as gold, silver and copper, fluorine-based resins such as PTFE (polytetrafluoroethylene), and DLC.
(Diamond-like carbon) and the like.

As the above-mentioned special surface treatment, for example, manganese phosphate treatment is cited. In this manganese phosphate treatment, the surface of the object to be treated is washed, degreased with alkali, washed with ion-exchanged water, and then pretreated with a surface conditioner to prepare an aqueous solution of the manganese phosphate compound on the surface of the object to be treated. The film forming treatment used is applied. As a result, on the surface of the object to be treated, surface corrosion due to the manganese phosphate salt compound and precipitation of crystals of the manganese phosphate salt on the surface will occur, and on the surface of the object to be treated,
Due to the surface corrosion action, minute and shallow irregularities (initial irregularities) are formed, and a coating film made of manganese phosphate is formed on the entire surface. On the surface of the object to be treated before the formation of this coating, relatively large irregularities are unevenly distributed, but due to the corrosive action, the uneven irregularities are reduced to small irregularities that exist evenly. It Further, the coating film is also formed by waviness following the surface irregularities of the object to be treated. Since the coating film having such unevenness has the required lubricity, the initial conformability is ensured, and lubricating components such as oil are retained in the valleys of the unevenness of the corrugated film. Therefore, long-term smooth operation is ensured.

[0053]

According to the eccentric thrust bearing of the present invention, a ball unit such as a so-called full ball bearing is used to improve the load resistance, smoothness of operation and wear resistance, and the center of the fixing member is used. The eccentric rotation of the movable member with reference to the above allows the ball unit to eccentrically rotate by following the movable member without play. for that reason,
The eccentric turning locus of the cage ring becomes regular, and the ball behavior of the ball unit becomes stable and difficult to slip. Therefore, it is possible to stabilize the operation of the movable member,
It can contribute to the improvement of bearing life.

[Brief description of drawings]

FIG. 1 is a sectional view of a scroll compressor using an eccentric thrust bearing according to an embodiment of the present invention.

FIG. 2 is an exploded perspective view of an eccentric thrust bearing.

FIG. 3 is a plan view showing the internal structure of an eccentric thrust bearing.

FIG. 4 is a cross-sectional view taken along the line (4)-(4) of FIG.

FIG. 5 is a view showing a state in which the movable race is eccentric in FIG.

FIG. 6 is a schematic diagram used to explain the operation of an eccentric thrust bearing.

FIG. 7 is an exploded perspective view of an eccentric thrust bearing according to another embodiment of the present invention.

8 is a plan view showing the internal structure of the eccentric thrust bearing of FIG.

9 is a plan view corresponding to FIG. 3, showing an example in which three through holes are provided.

10 is a plan view corresponding to FIG. 3, showing a modification of the insertion form of the movable pin and the fixed pin into the through hole.

11 is a plan view corresponding to FIG. 8 showing a modified example of the insertion form of the movable pin and the fixed pin into the through hole.

FIG. 12 is a cross-sectional view corresponding to FIG. 4 in a modification in which the through hole has two circular recesses.

[Explanation of symbols]

3 Orbiting scroll members 4 Fixed scroll member 10 Eccentric thrust bearing 11 Movable race 12 fixed race 13 ball unit 14 cage ring 15 balls 16a, 16b fan-shaped window of cage ring 20 Connecting part of cage ring 22 and 23 through hole of connecting part 30,31 Movable race pins 40,41 fixed race pins

   ─────────────────────────────────────────────────── ─── Continued front page    F term (reference) 3H029 AA02 AA12 BB32 BB33 BB44                       CC17                 3H039 AA01 BB04 BB07 BB28 CC18                       CC22                 3J101 AA02 AA32 AA42 AA53 AA62                       BA35 BA44 BA53 BA54 BA56                       DA02 DA03 EA02 EA31 EA44                       FA31 FA41 GA29

Claims (3)

[Claims] 1. An eccentric thrust bearing which is interposed between a movable member which makes an eccentric turning motion and a fixed member which is disposed so as to face the movable member in the axial direction, and which is eccentrically rotatable between both members. A retainer ring having a fan-shaped window extending axially through at least two locations on the circumference of the retainer ring;
A plurality of balls that are housed and retained in each fan-shaped window of the cage ring so as to be rotatable, and at least one circular recess is provided on each of the surfaces of the cage ring that face the movable member and the fixed member. A pin to be inserted into the first circular recess is provided in a portion of the movable member that faces the cage ring and that corresponds to the first circular recess, and the movable member is provided with a pin that is inserted into the first circular recess. A pin that is inserted into the second circular recess is provided at a portion of the surface of the fixed member that faces the cage ring and that corresponds to the second circular recess, and the pin on the movable member side and the fixed member are provided. The pins on the side are abutted against the inner peripheral wall surfaces of the corresponding circular recesses in a state of being arranged at a predetermined phase position on the circumference of the corresponding circular recesses, respectively, An eccentric thrust bearing in which the pin and the pin on the side of the fixing member are arranged to face each other by 180 degrees when assuming an imaginary situation in which the circular recesses are concentrically overlapped and arranged. 2. An eccentric thrust bearing which is interposed between a movable member which makes an eccentric turning motion and a fixed member which is disposed so as to face the movable member in the axial direction, and which is eccentrically rotatable between both members. A retainer ring having a fan-shaped window extending axially through at least two locations on the circumference of the retainer ring;
A plurality of balls that are housed and retained in each fan-shaped window of the cage ring so as to be rotatable, and a plurality of circular recesses are provided on each of the surfaces of the cage ring that face the movable member and the fixed member. The movable member and the fixed member are provided with pins to be inserted into the circular recesses, respectively, at portions corresponding to the circular recesses on the surface facing the cage ring. Each pin on the side is abutted against the inner peripheral wall surface of the corresponding circular recess in a state in which the pins are arranged at the same phase position on the circumference of each circular recess, and the fixing member side Each of the pins is abutted against the inner peripheral wall surface of the corresponding circular recess in a state in which the pins are arranged at the same phase position on the circumference of the circular recess, and the pins on the movable member side The above An eccentric thrust bearing in which the positional relationship with each pin on the side of the fixing member is set to be 180 degrees opposite to each other when an imaginary situation in which the circular recesses are concentrically overlapped and arranged is assumed. 3. The eccentric thrust bearing according to claim 1 or 2, further comprising a movable race fixed to the movable member and a fixed race fixed to the fixed member, and the ball unit between the races. An eccentric thrust bearing which is eccentrically rotatably interposed and in which the pins are provided on both races.