JP2008101763A - Retainer for thrust roller bearing, thrust roller bearing, and rotary shaft support structure for compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust roller bearing which employs a retainer for a thrust roller bearing reducing an axial thickness dimension while retaining rigidity and which has excellent lubricity. <P>SOLUTION: The thrust roller bearing 11 includes rollers, an inner circumference annular part 14, an outer circumference annular part 15, and a plurality of columns 16 radially arranged between the inner circumference annular part 14 and the outer circumference annular part 15, and is provided with a metal retainer 13 having a plurality of pockets 18 storing the rollers formed between the adjoining cage bars 16. The column 16 is provided with a recess part 19 for retaining lubricating oil on at least one wall surface of one and another side in a thickness direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a thrust roller bearing used in an automatic transmission, a compressor, and the like, and a thrust roller bearing retainer employed in such a thrust roller bearing.

  A thrust roller bearing used for an automatic transmission or a compressor of an automobile is described in, for example, Japanese Patent Laid-Open No. 9-79269 (Patent Document 1). Referring to FIG. 11, a thrust roller bearing 101 described in the publication includes a needle roller 102 (not shown in FIG. 11), an inner peripheral annular portion 103, an outer peripheral annular portion 104, and an inner peripheral annular portion 103. A retainer 107 having a plurality of pillars 105 arranged radially between the outer peripheral annular part 104 and a pocket 106 for accommodating the needle rollers 102 between the neighboring pillars 105. Prepare.

  The thrust roller bearing 101 having the above configuration has an advantage that a high load capacity and high rigidity can be obtained although the bearing projected area is small because the roller 102 and the raceway surface are in line contact.

  The cage 107 having the above-described configuration is a resin cage that is manufactured by injection molding a synthetic resin that is excellent in productivity and economy. Referring to FIG. 12, the column portion 105 includes a meat stealing portion 108 that reduces the thickness of the column portion 105 on one side wall surface, and a roller that prevents the needle roller 102 from falling off on the wall surface facing the pocket 106. A stop 109 is formed.

The thrust roller bearing 101 described in the above publication can improve the elastic deformability of the roller stopper 109 by providing the meat stealer 108 at a position adjacent to the roller stopper 109 of the cage 107. As a result, it is described that the resistance at the time of injection molding can be reduced.
Japanese Patent Laid-Open No. 9-79269

  In recent years, the downsizing of automatic transmissions, compressors, and the like has progressed, and accordingly, there is a strong demand for reducing the axial thickness of the thrust roller bearing 101 used in these devices.

  Here, in order to reduce the axial thickness dimension of the thrust roller bearing 101, the plate thickness of the cage 107 must be reduced. However, the cage 107 made of synthetic resin has a limit in reducing the thickness dimension from the viewpoint of securing rigidity. This is particularly remarkable in the large-diameter thrust roller bearing 101.

  In recent years, the amount of lubricating oil in driving parts such as automatic transmissions and compressors has been reduced with the reduction of automobile emissions. Furthermore, lubricating oils with low viscosity and containing additives are used. Since such lubricating oil has a low lubricating performance, the oil film is cut at the contact portion, and surface damage and surface-origin type peeling are likely to occur. As a result, there is a need for a thrust roller bearing that can be used under lean lubrication.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a thrust roller bearing having excellent lubricity as well as adopting a thrust roller bearing retainer having a reduced axial thickness while maintaining rigidity.

  Another object of the present invention is to provide a rotary shaft support structure for a compressor having excellent lubricity and high reliability.

  A thrust roller bearing according to the present invention includes a roller, an inner circumferential annular portion, an outer circumferential annular portion, a plurality of column portions arranged radially between the inner circumferential annular portion and the outer circumferential annular portion, and one thickness direction of the column portions. And a metal cage having a recess for holding lubricating oil on at least one wall surface of the side and the other side, and having a plurality of pockets for accommodating rollers between adjacent column portions.

  Since the thrust roller bearing having the above-described configuration is provided with the recess for retaining the lubricating oil on the wall surface of the cage, the oil retaining property is improved. In the present specification, “oil retention” refers to the property that lubricating oil supplied from the outside stays inside the bearing. That is, in the thrust bearing having the above-described configuration, the lubricating oil supplied from the outside remains in the recess as an oil sump provided in the cage. Since the lubricating oil gradually flowing out from the recess lubricates the rolling surface of the roller, a thrust roller bearing having excellent lubricity can be obtained even under lean lubrication.

  Here, high oil permeability is required for the thrust roller bearing used in an environment where a sufficient amount of lubricating oil is supplied. In other words, it is important to remove dust and wear powder inside the bearing and to prevent an increase in stirring resistance due to the lubricant by smoothing in and out of the lubricant.

  On the other hand, for thrust roller bearings used under lean lubrication, it is important to always keep the lubricating oil inside the bearing so that the lubricating oil can be constantly supplied to the rolling surface of the roller. That is, it can be said that the thrust roller bearing according to the present invention is suitable for use in a lean lubrication environment.

  The cage employed in the thrust roller bearing having the above-described configuration is a metal cage formed of a metal material such as steel. Thereby, even if it reduces thickness dimension, the rigidity required for a holder | retainer can be maintained. That is, it can be said that the thrust roller bearing according to the present invention is suitable for use in equipment that is becoming more compact, such as automatic transmissions and compressors.

  In one embodiment, the pocket has a roller stopper that prevents the roller from falling off. And a recessed part and a stop part are arrange | positioned on the same circumference centering on the rotating shaft center of a holder | retainer at the same wall surface side of the thickness direction of a holder | retainer.

  Preferably, each pillar part has the said several recessed part. Thereby, the oil retention amount of the thrust roller bearing further increases.

  More preferably, the plurality of concave portions provided in each column portion are provided at positions shifted in the radial direction of the cage. Thereby, lubricating oil can be more uniformly supplied to the rolling surface of each roller.

  A cage for a thrust roller bearing according to the present invention includes an inner circumferential annular portion, an outer circumferential annular portion, a plurality of column portions radially disposed between the inner circumferential annular portion and the outer circumferential annular portion, and a thickness direction of the column portion. A recess for holding lubricating oil is provided on at least one wall surface of the one side and the other side. The thrust roller bearing cage is made of a metal material.

  A compressor rotation shaft support structure according to the present invention includes a rotation shaft and the thrust roller bearing that supports a thrust load generated by the rotation of the rotation shaft. By adopting the above thrust roller bearing, it is possible to obtain a rotary shaft support structure for a compressor having excellent lubricity and high reliability.

  According to the present invention, by providing the concave portion on the wall surface of the cage, the thrust roller bearing cage having high oil retaining property and the use of such a cage have excellent lubricity even under lean lubrication. A thrust roller bearing can be obtained.

  Further, by forming the cage with a metal material, the rigidity can be maintained even if the thickness dimension is reduced. As a result, it is possible to obtain a thrust roller bearing suitable for use in equipment that is becoming more compact.

  Furthermore, according to the present invention, by adopting the thrust roller bearing as described above, it is possible to obtain a compressor rotation shaft support structure that is excellent in lubricity and highly reliable.

  With reference to FIGS. 1-5, the thrust roller bearing 11 and the thrust roller bearing retainer 13 which concern on one Embodiment of this invention are demonstrated. 1 is a front view of the thrust roller bearing 11, FIG. 2 is a rear view of the thrust roller bearing 11, FIG. 3 is a sectional view taken along the line III-III in FIG. 1, and FIG. 4 is a sectional view taken along the line IV-IV in FIG. FIG. 5 is an enlarged view of a portion P in FIG.

  A thrust roller bearing 11 according to an embodiment of the present invention includes a plurality of rollers 12 and a cage and roller provided with a thrust roller bearing retainer 13 (hereinafter referred to as “retainer 13”) that retains the plurality of rollers 12. Type of bearing.

  With reference to FIGS. 1 and 2, the retainer 13 includes an inner circumferential annular portion 14, an outer circumferential annular portion 15 positioned on the radially outer side of the inner circumferential annular portion 14, an inner circumferential annular portion 14, and an outer circumferential annular portion 15. And the column parts 16 arranged radially. In addition, recesses 17a, 17b, and 17c (hereinafter collectively referred to) are provided on the front surface (referred to as “wall surface on one side in the thickness direction”) and the back surface (referred to as “wall surface on the other side in the thickness direction)”, respectively. (Referred to as “concave portion 17”). Further, a plurality of pockets 18 for holding the roller 12 in a rollable manner are formed between the adjacent column portions 16.

Referring to FIG. 1, the concave portions 17 a and 17 b on the surface of the cage 13 are provided at two positions on each column portion 16 with the radial positions shifted. Specifically, it includes an inner peripheral recess 17a provided on the radially inner side and an outer peripheral recess 17b provided on the radially outer side. The plurality of inner peripheral recesses 17 a and outer peripheral recesses 17 b are positioned on the circumferences of the circles c ₁ and c ₂ centering on the rotation axis of the thrust roller bearing 11. Moreover, in this embodiment, the recessed part 17 is a rectangular shape.

On the other hand, referring to FIG. 2, the concave portion 17 c on the back surface of the cage 13 is provided in the central portion in the radial direction of each column portion 16 (referred to as “central concave portion 17 c”). The plurality of central recesses 17 c are located on the circumference of a circle c ₃ centering on the rotational axis of the thrust roller bearing 11.

  The pocket 18 is a rectangular through-hole penetrating in the thickness direction of the cage 13. And it arrange | positions radially toward the radial direction of the holder | retainer 13 in a longitudinal direction. 3 and 4, the pocket 18 is provided with a plurality of roller stoppers 19 that protrude from the wall surface facing the rolling surface of the roller 12.

  Specifically, the first and second roller stoppers 19a and 19b (only the first roller stopper 19a is shown in FIG. 3) unevenly distributed on one side (surface side) in the thickness direction of the cage 13 and the other side (back surface). 3rd roller stopper 19c unevenly distributed to the side). These roller stoppers 19 prevent the rollers 12 accommodated in the pockets 18 from dropping off to one side and the other side of the cage 13 in the thickness direction.

  Further, the wall surface of each roller stopper 19 that faces the roller 12 has a tapered shape in order to prevent the corner from attacking the roller 12. Furthermore, the wall surface between the roller stoppers 19a, 19b on one side in the thickness direction of the cage 13 and the roller stopper 19c on the other side functions as a guide surface 18a for guiding the rotation of the roller 12.

  Next, referring to FIG. 5, the inner peripheral concave portion 17 a, the outer peripheral concave portion 17 b, and the central concave portion 17 c are provided at positions shifted in the radial direction. Similarly, the first roller stopper 19a, the second roller stopper 19b, and the third roller stopper 19c are also provided at positions shifted in the radial direction.

  Further, the inner peripheral recess 17a and the outer peripheral recess 17b, and the first and second roller stoppers 19a, 19b are provided on the same wall surface side (surface side) of the cage 13. On the other hand, the central recess 17c and the third roller stopper 19c are provided on the same wall surface side (back surface side) of the cage 13.

Further, the first roller stopper portion 19a is on the circumference of a circle _{c 1} provided in the respective pockets 18, the second roller stoppers 19b on the circumference of a circle _{c 2,} third roller stoppers 19c circle c ₃ are arranged on the circumference of ₃ respectively. That is, the inner circumferential recess 17a and the first roller stopper 19a, the outer recess 17b and the second roller stopper 19b, and the central recess 17c and the third roller stopper 19b are the same in the thickness direction of the cage 13. Located on the wall and on the same circumference.

  The cage 13 having the above configuration is a metal cage formed of a metal material such as steel. Further, the plate thicknesses of the inner peripheral annular portion 14, the outer peripheral annular portion 15, and the column portion 16 are substantially uniform. Further, the roller stopper 19 does not protrude from the front and back surfaces of the cage 13. Therefore, the cage 13 has a flat shape as a whole. As a method for manufacturing such a cage 13, for example, the above-described configuration is obtained by pressing one steel plate. Specifically, the outer shape of the cage 13 is formed by punching and the pocket 18 is punched.

  Further, as described above, when the concave portion 17 and the stopper portion 19 are provided on the same wall surface side in the thickness direction of the cage 13 and on the same circumference, the concave portion 17 is formed simultaneously with the coining process. A roller stopper 19 adjacent to each of the recesses 17 can be formed by the surplus that has occurred.

  On the other hand, the roller 12 is a cylindrical rolling element having a rolling surface 12a. The roller 12 rotates and rotates around the rotation axis of the thrust roller bearing 11 when the bearing rotates. At that time, the rolling surface 12a contacts the raceway surface (not shown) and the inner wall surface of the pocket 18 (including the roller stopper 19).

  Therefore, it is necessary to supply lubricating oil between the rolling surface 12 a and the raceway surface and between the rolling surface 12 a and the inner wall surface of the pocket 18. In the case of a cage & roller type bearing, the raceway surface is provided on the device side in which the thrust roller bearing 11 is incorporated.

  In the thrust roller bearing 11 configured as described above, the lubricating oil supplied from the outside remains in the recess 17 as an oil pool provided in the cage 13. Then, the lubricating oil gradually flowing out from the recess 17 lubricates the rolling surface of the roller 12. That is, the oil retaining property of the thrust roller bearing 11 is improved by providing the retainer 13 with the recess 17. As a result, it is possible to obtain the thrust roller bearing 11 having excellent lubricity even under lean lubrication.

  The concave portion 17 is a non-through concave portion having a bottom wall. Further, the periphery is surrounded by a side wall, which is different from the groove communicating with the adjacent pocket 18. By adopting such a configuration, not the oil permeability but the oil retaining property is improved.

  Further, by providing a plurality of recesses 17a, 17b, and 17c in each column part 16, the oil retaining property of the thrust roller bearing 11 is further improved as compared with the case of one place. Further, by providing the plurality of recesses 17 a, 17 b, and 17 c at positions shifted in the radial direction of the cage 13, the lubricating oil can be evenly supplied to the rolling surface of the roller 12.

  In addition, the first and second roller stoppers 19 a and 19 b provided on one side in the thickness direction of the cage 13 and the third roller stopper 19 c provided on the other side are shifted in a radial direction of the cage 13. By providing, the roller 12 can be appropriately held.

  Furthermore, the cage 13 employed in the thrust roller bearing 11 having the above-described configuration is a metal cage. Thereby, even if it reduces thickness dimension, the rigidity required for the holder | retainer 13 can be maintained. In other words, it can be said that the thrust roller bearing 11 is suitable for use in devices that are becoming more compact, such as automatic transmissions and compressors.

  In the above-described embodiment, an example in which two concave portions 17 are provided on the front surface side of each pillar portion 16 and one concave portion 17 is provided on the rear surface side is not limited thereto. Can be provided.

  Further, in the above embodiment, the example in which the concave portion 17 is provided on the wall surface in the thickness direction of each column portion 16 has been shown. However, from the viewpoint of improving the oil retaining property of the thrust roller bearing 11, any position, i. A recess may be provided in the circumferential annular portion 14 or the outer circumferential annular portion 15. However, from the viewpoint of properly supplying the lubricating oil to the rolling contact surface 12a of the roller 12, it is desirable to provide the pillar 16 adjacent to the rolling contact surface 12a.

  Moreover, although the recessed part 17 in said embodiment showed the example which is a rectangular shape, it can be set as arbitrary shapes, without restricting to this. For example, the thrust roller bearing retainer 23 shown in FIG. 6 has circular recesses 27a and 27b. The thrust roller bearing retainer 33 shown in FIG. 7 has oval recesses 37a and 37b extending in the circumferential direction. The thrust roller bearing retainer 43 shown in FIG. 8 has an elliptical recess 47 extending in the radial direction. In FIGS. 6 and 7, the recesses 27a and 27b and the recesses 37a and 37b are arranged at positions shifted in the radial direction.

  In the thrust roller bearing retainers 13, 23, 33 in each of the above-described embodiments, the width of the column parts 16, 26, 36 increases from the radially inner side to the radially outer side. For this reason, the area of the outer peripheral recesses 17b, 27b, and 37b is larger than that of the inner peripheral recesses 17a, 27a, and 37a.

  On the other hand, the lubricating oil inside the bearing is unevenly distributed radially outward due to the centrifugal force when the bearing rotates. For this reason, it is desirable to increase the oil retaining amount of the inner peripheral recesses 17a, 27a, 37a and improve the oil retaining property on the inner peripheral side of the thrust roller bearing retainers 13, 23, 33.

  Therefore, for example, if the oil retaining amount is increased by making the depth of the inner peripheral recesses 17a, 27a, and 37a deeper than the outer peripheral recesses 17b, 27b, and 37b, the roller rolling surfaces of the rollers are more evenly lubricated. Oil can be supplied.

  The basic configuration of the thrust roller bearing cages 23, 33, and 43 having the above configuration is the same as that of the cage 13, and thus detailed description thereof is omitted.

  In the above embodiment, an example of the cage & roller type thrust roller bearing 11 composed of the roller 12 and the cage 13 has been described from the viewpoint of reducing the thickness dimension. The invention can also be applied to a thrust roller bearing further having a race.

  With reference to FIG. 9, the thrust roller bearing 51 which concerns on other embodiment of this invention is demonstrated. In addition, since the structure of the roller 52 and the holder | retainer 53 is common with the thrust roller bearing 11, description of a common point is abbreviate | omitted and it demonstrates centering on difference.

  The thrust roller bearing 51 includes a plurality of rollers 52, a cage 53, and first and second race rings 54 and 55 disposed on one side and the other side in the thickness direction of the cage 53. The first and second rail wheels 54 and 55 are disk-shaped members having holes 54a and 55a formed in the center. The first rail wheel 54 has an inner peripheral flange 54b protruding in the axial direction at the inner edge thereof. The second rail wheel 55 has an outer peripheral flange 55b protruding in the axial direction at the outer edge thereof.

  The thrust roller bearing 52 configured as described above has a larger thickness than the cage and roller type thrust roller bearing 11. However, since the thrust roller bearing 11 must have a raceway surface in contact with the roller 12 on the equipment side, the number of work steps such as a polishing step increases. On the other hand, the thrust roller bearing 51 is provided with the race wheels 54 and 55, so that the polishing process on the device side can be omitted. Further, since the raceway surfaces of the race wheels 54 and 55 can be easily obtained as extremely smooth surfaces, the rollers 52 can smoothly rotate even under lean lubrication.

  In addition, as another example of the metal cage, there is a W-type cage in which a steel plate is bent in a thickness direction so that a cross-sectional shape is substantially W-shaped. In the W-type cage, it is difficult to reduce the thickness dimension while maintaining the rigidity of the cage because the plate thickness of the steel sheet must be reduced with respect to the thickness dimension of the cage. Therefore, it can be said that the flat thrust roller bearing retainer 13 in which the concave portion 17 and the pocket 18 are formed on the annular flat plate is suitable for the present invention.

  Further, the present invention can be applied to all types of thrust roller bearings having needle rollers, rod rollers, or cylindrical rollers as rollers. However, a thrust needle roller bearing is desirable from the viewpoint of reducing the thickness dimension.

  Next, a compressor 61 according to an embodiment of the present invention will be described with reference to FIG. The compressor 61 includes a casing 62, a rotating shaft 69, a swash plate 70, a piston 71, and an electromagnetic clutch 72. The compressor 61 is incorporated in a vapor compression refrigerator of an automobile air conditioner.

  The casing 62 includes a head case 63 having a low-pressure chamber 66 and a high-pressure chamber 67, a cylinder case 64 having a plurality of cylinders 68 in which the piston 71 reciprocates, and a swash plate case 65 for housing the swash plate 70 (bolts shown). (Omitted).

  The low-pressure chamber 66 has a suction port (not shown) provided in the head case 63, a suction hole 66a communicating with each cylinder 68, and a valve 66b for preventing the reverse flow of the refrigerant vapor from the suction hole 66a. The suction port communicates with the outlet of an evaporator (not shown) that constitutes the vapor compression refrigerator. Then, the refrigerant vapor sucked from the suction port is supplied to the cylinder 68 through the suction hole 68a.

  On the other hand, the high-pressure chamber 67 has a discharge port (not shown) provided in the head case 63, a discharge port 67a communicating with the cylinder 68, and a valve 67b for preventing the reverse flow of the refrigerant vapor from the discharge port 67a. The discharge port communicates with an inlet of a condenser (not shown) that constitutes the vapor compression refrigerator. Then, the refrigerant vapor inside the cylinder 68 compressed by the piston 71 is supplied to the high pressure chamber 67 through the discharge port 67a.

  The rotating shaft 69 communicates with the casing 62 and the electromagnetic clutch 72, and is rotatably supported at two locations, a cylinder case 64 and a swash plate case 65, by a radial needle roller bearing 69a and a thrust needle roller bearing 69b. A swash plate 70 is held inside the swash plate case 65.

  The swash plate 70 is fixedly connected to the rotation shaft 69 while being inclined at a predetermined angle with respect to a plane orthogonal to the rotation axis of the rotation shaft 69. Also, pistons 71 are connected to a plurality of locations on the circumference by a sliding shoe 70a.

  The piston 71 is connected to the swash plate 70, and reciprocates in the axial direction (left and right direction in FIG. 10) inside the cylinder 68 as the rotating shaft 69 rotates. A compression chamber 68a for compressing the refrigerant vapor is formed in a region surrounded by the cylinder 68 and the piston 71.

  The electromagnetic clutch 72 includes a pulley 73, a solenoid 74, a magnetic annular plate 75, and a pulley support bearing 76.

  The pulley 73 has a groove 73 b that holds the endless belt 73 a on the outer diameter surface, and a recess 73 c that houses the solenoid 74 on one end surface, and is rotatably supported by the casing 62 by a pulley support bearing 76.

  The solenoid 74 is disposed in a state where a predetermined gap is provided inside the recess 73 c and is fixed to the casing 62. The magnetic annular plate 75 is an annular member formed of a magnetic material, and is arranged so as to face the solenoid 74 with the pulley 73 interposed therebetween. Moreover, it is being fixed to the rotating shaft 69 by the leaf | plate spring 75a. The leaf spring 65 a biases the magnetic annular plate 75 in a direction away from the pulley 73.

  A gap is formed between the pulley 73 and the magnetic annular plate 75 when the solenoid 74 is not energized. As a result, the rotation of the pulley 73 is not transmitted to the rotating shaft 69. on the other hand. When the solenoid 74 is energized, the magnetic annular plate 75 abuts against the pulley 73 against the leaf spring 75a by the attraction force of the solenoid 74. As a result, the rotation of the pulley 73 is transmitted to the rotating shaft 69 via the rotor 73.

  When the rotating shaft 69 rotates, the piston 71 attached to the swash plate 70 reciprocates inside the cylinder 68. When the piston 71 moves in the direction of increasing the volume of the compression chamber 68a (left direction in FIG. 10), the valve 66b is opened, and the refrigerant vapor moves from the low pressure chamber 66 through the suction hole 66a to the compression chamber 68a. At this time, the valve 67b is closed to prevent the refrigerant vapor in the high pressure chamber 67 from flowing back to the compression chamber 68a.

  Next, when the piston 71 moves in the direction of reducing the volume of the compression chamber 68a (the right direction in FIG. 10), the piston 71 compresses the refrigerant vapor in the compression chamber 68a and the valve 67b is opened to be compressed. The refrigerant vapor thus moved moves to the high pressure chamber 67 through the discharge port 67a. At this time, the valve 66b is closed to prevent the refrigerant vapor in the compression chamber 68a from flowing back to the low pressure chamber 66.

  In the compressor 61 having the above-described configuration, the thrust shaft due to the reciprocating motion of the piston 71 is applied to the rotating shaft 69. In addition, the amount of lubricating oil enclosed in the compressor 61 is reduced as compared with the prior art as the emission of automobiles is reduced. Therefore, the thrust roller bearings 11, 21, 31, 41, 51 according to the embodiment of the present invention are employed as the thrust roller bearing 69b that supports the thrust load generated on the rotating shaft 69. Thereby, it is possible to obtain a compressor rotation shaft support structure having excellent lubricity and high reliability.

  In addition, although the compressor 61 in said embodiment showed the example of the swash plate type which provided the piston 71 only in the one side of the axial direction, it is not limited to this Example. The present invention can also be applied to a double swash plate type in which pistons are provided on both sides in the axial direction, or a variable capacity swash plate type compressor in which the angle of the swash plate can be changed.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The present invention is advantageously used for thrust roller bearings used in automatic transmissions, compressors and the like.

It is a surface view of the thrust roller bearing which concerns on one Embodiment of this invention. It is a surface view of the thrust roller bearing which concerns on one Embodiment of this invention. It is sectional drawing in III-III of FIG. It is sectional drawing in IV-IV of FIG. It is an enlarged view of the P section of FIG. It is a figure which shows the other form of the cage for thrust roller bearings concerning this invention. It is a figure which shows the other form of the cage for thrust roller bearings concerning this invention. It is a figure which shows the other form of the cage for thrust roller bearings concerning this invention. It is a figure which shows the thrust roller bearing which concerns on other embodiment of this invention. It is a figure which shows the compressor which concerns on one Embodiment of this invention. It is a front view of the conventional thrust roller bearing. It is sectional drawing containing the pocket of the thrust roller bearing of FIG.

Explanation of symbols

11, 21, 31, 41, 51, 101 Thrust roller bearing, 12, 52, 102 roller, 12a Rolling surface, 13, 23, 33, 43, 53, 107 Cage, 14, 103 Inner ring portion, 15 104, 26, 36, 105 pillar part, 17, 17a, 17b, 17c, 27a, 27b, 37a, 37b, 47 recess, 18, 106 pocket, 18a guide surface, 19, 19a, 19b, 19c, 109 Roller stop, 54, 55 raceway, 54a, 55a hole, 54b, 55b collar, 61 compressor, 62 casing, 63 head case, 64 cylinder case, 65 swash plate case, 66 low pressure chamber, 66a suction hole , 66b, 67b valve, 67 high pressure chamber, 67a discharge port, 68 cylinder, 68a compression chamber, 69 rotating shaft, 69a Radial needle roller bearing, 69b thrust needle roller bearing, 70 swash plate, 70a sliding shoe, 71 piston, 72 electromagnetic clutch, 73 pulley, 73a endless belt, 73b groove, 73c recess, 74 solenoid, 75 magnetic annular plate, 75a Leaf spring, 76 pulley support bearing, 108 meat stealer.

Claims (6)

And
At least one of an inner peripheral annular part, an outer peripheral annular part, a plurality of pillar parts arranged radially between the inner peripheral annular part and the outer peripheral annular part, and one side and the other side in the thickness direction of the pillar part A thrust roller bearing comprising: a metal retainer having a concave portion for retaining lubricating oil on a wall surface thereof and having a plurality of pockets for accommodating the rollers between the adjacent column portions. The pocket has a roller stopper for preventing the roller from falling off,
The said recessed part and the said roller stop part are the same wall surface side of the thickness direction of the said holder | retainer, and are arrange | positioned on the same periphery centering on the rotating shaft center of the said holder | retainer. Thrust roller bearing.   The thrust roller bearing according to claim 1, wherein each of the column portions includes a plurality of the concave portions.   The thrust roller bearing according to claim 3, wherein the plurality of recesses provided in each column part are provided at positions shifted in a radial direction of the cage. An inner ring portion,
A peripheral annular portion;
A plurality of pillars arranged radially between the inner peripheral annular part and the outer peripheral annular part;
A concave portion for holding lubricating oil on at least one wall surface of the pillar portion in the thickness direction on one side and the other side;
Thrust roller bearing cage made of metal material. A rotation axis;
A rotary shaft support structure for a compressor, comprising a thrust roller bearing according to any one of claims 1 to 4, which supports a thrust load generated by the rotation of the rotary shaft.

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