JP2008002503A - Thrust roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust roller bearing capable of effectively preventing wear of points of contact between the roller and a retainer. <P>SOLUTION: The thrust roller bearing 11 comprises a plurality of rollers 12 having a curved surface to swell in a rolling element shaft center direction to an end surface, a plurality of pockets 17 which is a circular plate member which has a hole 14 in the center to accommodate rollers by passing completely through to the other in the thickness direction and the retainer 13 including a peripheral collar portion 18 extending in the axial direction along the outer periphery of the circular plate, while being located diametrically outside of the wall surface 17d in the diametric outside of the pocket 17. Additionally, the outer peripheral collar portion 18 has a guide way 18a to guide the end surface of the rollers 12 in the wall surface of the diametric inside and in the territory from the outer periphery collar portion 18 to the pocket 17, a plate 17e inclined toward the wall surface 17d diametrically outside of the pocket 17 from the guide way 18a is provided. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a thrust roller bearing, and more particularly to a thrust roller bearing used in a car air conditioner compressor, an automatic transmission, a manual transmission, a hybrid vehicle, and the like.

  In recent years, compressors for car air conditioners, automatic transmissions, manual transmissions, hybrid vehicles, and the like have been reduced in size and output, and thrust roller bearings incorporated therein are also required to support higher speeds. On the other hand, the amount of lubricating oil has been reduced and low-viscosity lubricating oil has been used to reduce fuel consumption in consideration of the environment, and the use conditions of thrust roller bearings have been severe. For this reason, there is a problem of wear (drilling wear) that occurs at the contact portion between the end face facing the radially outer side of the roller and the pocket wall surface when the bearing rotates.

  Thus, thrust roller bearings used in such an environment are described in, for example, Japanese Patent Application Laid-Open No. 2003-83333 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2004-301195 (Patent Document 2). Referring to FIG. 8, the thrust roller bearing 101 described in each of the above publications holds a plurality of rollers 102, race rings 103 and 104 that sandwich the plurality of rollers in the axial direction, and a plurality of rollers 102. And a cage 105. The cage 105 has a pair of annular portions 105a and 105b and a plurality of pocket portions 105c formed between the annular portions 105a and 105b. The pocket portion 105c extends to the annular portion 105a on the outer diameter side. is doing.

  Moreover, as a manufacturing method of the cage 105 having the above-described configuration, pocket punching is performed on the steel sheet so as to form a pocket portion 105c that holds the rollers. Thereafter, the inner diameter side is bent outward to form the inner diameter side annular portion 105b. Furthermore, the cage 105 in which the pocket portion 105c extends to the annular portion 105a on the outer diameter side can be manufactured by bending the outer diameter side in the opposite direction inside the outer diameter side end portion of the pocket portion 105c. it can.

The thrust roller bearing 101 configured as described above rotates while the end surface facing the radially outer side of the roller 102 is in contact with the radially inner wall surface of the annular portion 105a, so that it contacts the outer diameter side end portion 105d of the pocket portion 105c. The contact area increases compared to the case. As a result, it is described that wear between the roller 102 and the cage 105 can be effectively suppressed even under severe lubrication conditions.
JP 2003-83333 A JP 2004-301195 A

  In the above manufacturing method, since the bending process is performed after the pocket part 105c is formed, the pocket part 105c at the time of the bending process may be deformed. This can cause a rotation failure of the rollers 102 accommodated in the pocket portion 105c.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a thrust roller bearing having a shape in which the cage is easily processed and capable of effectively suppressing wear of a contact portion between the roller and the cage.

  A thrust roller bearing according to the present invention is a disc-shaped member having a plurality of rollers having curved surfaces bulging in the rolling axis direction on the end surface and a hole formed in the center, and penetrates in the thickness direction. A plurality of pockets for storing the rollers, and a cage that is located on the radially outer side of the radially outer wall surface of the pocket and includes an outer peripheral flange that extends in the axial direction along the outer periphery of the disk. The outer peripheral flange has a guide surface for guiding the end face of the roller on the radially inner wall surface, and the region extending from the outer peripheral flange to the pocket is directed from the outer peripheral flange to the radially outer wall surface of the pocket. An inclined surface that is inclined is provided.

  In the thrust roller bearing configured as described above, the top of the curved surface formed on the end surface of the roller contacts with the guide surface formed on the radially inner wall surface of the outer peripheral flange when the bearing rotates. Here, the peripheral speed of the end face of the roller has the smallest rolling axis (center of the roller diameter) of the roller and increases toward the outer side in the radial direction. Therefore, by matching the rolling axis at the top of the curved surface, the PV value of the contact portion between the roller end surface and the cage guide surface can be reduced, and wear of the contact portion can be effectively suppressed. it can. The “PV value” refers to a value obtained by multiplying the contact surface pressure P (MPa) between the roller end surface and the cage guide surface by the sliding speed V (m / min).

  In addition, the cage having the above-described configuration can be punched in the pocket after the shape of the cage is formed by bending, so that high-precision machining is easy to perform. Further, by providing the inclined surface, it is possible to prevent the end surface of the roller from coming into contact with the wall surface on the radially outer side of the pocket even if the region extending from the outer peripheral flange portion to the pocket is enlarged. As a result, a thrust roller bearing with reduced manufacturing costs can be obtained.

Preferably, the retainer plate thickness of t _0, when the thickness of the radially outer wall surface of the pocket and t, satisfy t / t 0> _1/3. More preferably, the inclination angle θ of the inclined surface with respect to the guide surface satisfies 30 ° ≦ θ ≦ 60 °. From the viewpoint of preventing the end face of the roller from coming into contact with the radially outer wall surface of the pocket, the thickness dimension t of the radially outer wall surface of the pocket should be small, but in order to maintain the rigidity required for the cage Should satisfy the above ranges.

  According to the present invention, it is possible to obtain a thrust roller bearing having a shape in which the cage is easily processed and capable of effectively suppressing wear of a contact portion between the roller and the cage.

  With reference to FIG. 1 and FIG. 2, the thrust roller bearing 11 which concerns on one Embodiment of this invention is demonstrated. 1 is a plan view of a thrust roller bearing 11 according to an embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along line II-II in FIG.

  The thrust roller bearing 11 is a cage-and-roller type bearing having a plurality of rollers 12 and a retainer 13 that holds the interval between adjacent rollers 12, and mainly includes a compressor for an car air conditioner, an automatic transmission, a manual transmission, And used in hybrid vehicles.

  The roller 12 is a cylindrical roller having a cylindrical rolling surface and end surfaces having curved surfaces bulging in the direction of the rolling axis at both end surfaces. The end face shape is an A end face or an AR end face defined by JIS standards (Japan Industrial Standards: B 1506), and the top of the curved surface formed on the end face coincides with the rolling axis of the roller 12.

  The cage 13 is a disk-shaped member having a hole 14 formed in the center, and is formed by bending a metal flat plate by pressing or the like. And between the inner periphery collar part 15 formed along the outer periphery of the hole 14, the outer periphery collar part 18 formed along the outer periphery of the holder | retainer 13, and the inner periphery collar part 15 and the outer periphery collar part 18, it is a roller. A plurality of pockets 17 for accommodating 12 are formed, and has a roller holding portion 16 extending in the radial direction.

  The inner peripheral flange portion 15 is formed by being bent by a predetermined length toward one side in the thickness direction of the cage 13 and then folded back by 180 °. Further, the wall surface facing the hole 14 of the inner peripheral flange 15 functions as a guide surface 15a that guides the shaft when it is incorporated into the rotating shaft. In the present invention, the inner peripheral flange 15 is not an essential component, but the rigidity of the cage 13 is improved by providing the inner peripheral flange 15.

  The roller holding portion 16 extends in the radial direction while being bent in the thickness direction of the cage 13, and a plurality of pockets 17 penetrating in the thickness direction are arranged radially with respect to the bearing rotation axis with the longitudinal direction directed in the radial direction. Has been.

  The pocket 17 has a rectangular shape along the outer shape of the roller 12, and the wall surface facing the rolling surface of the roller 12 in the pocket 17 is the axial direction of the roller 12 at the radial center of one side in the thickness direction of the cage 13. A first retaining portion 17a for preventing the roller 12 from coming off; a second retaining portion 17b for preventing the roller 12 from coming off to the other side in the axial direction at both ends in the radial direction on the other side in the thickness direction of the cage 13; And an inclined portion 17c for connecting the first and second retaining portions 17a and 17b.

  The first and second retaining portions 17a and 17b protrude from the wall surface on one side in the longitudinal direction of the pocket 17 toward the wall surface on the other side, abut against the rolling surface of the roller 12, and the axial direction of the cage 13 Regulate displacement.

  The outer peripheral flange 18 is positioned further radially outward of the wall 17d on the radially outer side of the pocket 17, and is bent by a predetermined length toward one side in the thickness direction of the cage 13 like the inner peripheral flange 15. , 180 ° folded back. The rigidity of the cage 13 is also improved by providing the outer peripheral flange 18. Further, a guide surface 18 a for guiding the end surface of the roller 12 is formed on the radially inner wall surface of the outer peripheral flange portion 18.

  Next, with reference to FIG. 3 and FIG. 4, the relationship between the end surface of the roller 12 and the guide surface 18a provided in the outer periphery collar part 18 is demonstrated. 3 is an enlarged view of a portion P in FIG. 1 and a portion Q in FIG. 2, and shows a state in which the end surface of the roller 12 and the guide surface 18a are not in contact with each other. FIG. FIG. 3 is an enlarged view of a portion Q in FIG. 2 and shows a state where an end surface of a roller 12 and a guide surface 18a are in contact with each other. In both figures, the upper part shows a plan view and the lower part shows a side sectional view.

  First, referring to FIG. 3, the length of the pocket 17 in the longitudinal direction is slightly longer than the length of the roller 12. Therefore, when the bearing is stopped, the end surface of the roller 12 on the radially outer side and the outer peripheral flange 18. In some cases, the guide surface 18a is not in contact.

  The guide surface 18a indicates a cylindrical portion extending in the direction of the bearing rotation axis excluding bent portions at both ends of the wall surface on the radially inner side of the outer peripheral flange portion 18, and its axial length is L, the roller diameter of the roller 12. Is set so as to satisfy L / D> 0.3.

  The cage 13 serves as a roller guide by providing the pocket 17 with first and second retaining portions 17a, 17b. Therefore, if the axial length L of the guide surface 18a is short, the end surface of the roller 12 may be detached from the guide surface 18a when the cage 13 is biased in the axial direction. Therefore, by setting the axial length L of the guide surface 18a to be longer than the axial displacement amount of the cage 13, the end surface of the roller 12 can always be in contact with the guide surface 18a during the bearing rotation. The amount of axial displacement of the cage 13 can be adjusted by the amount of protrusion of the retaining portions 17a and 17b.

On the other hand, in order to rolling surface of the roller 12 is in contact with both sides in the thickness direction of the raceway surface of the thrust roller bearing 11 is required to be smaller than the thickness L ₀ Gakoro diameter D of the retainer 13. Further, in the cage 13 manufactured by press working, it is difficult to eliminate the bent portions at both ends of the guide surface 18a. Therefore, the axial length L of the guide surface 18a needs to be set within a range satisfying L <L ₀ <D.

  Further, by using the cage 13 as a roller guide, the wall surface in the thickness direction of the cage 13 and the raceway surface are not in contact with each other, so torque loss during rotation of the bearing can be suppressed and the thickness of the cage 13 can be suppressed. Oil permeability between the direction wall surface and the raceway surface is improved. Thereby, it is possible to reduce the amount of heat generated when the bearing rotates.

  Next, referring to FIG. 4, the roller 12 moves radially outward by centrifugal force accompanying the rotation of the thrust roller bearing 11. At this time, the end surface of the roller 12 is in contact with only the guide surface 18 a provided on the outer peripheral flange 18, and is not in contact with the radially outer wall surface 17 d of the pocket 17. Specifically, the top of the curved surface provided on the end surface of the roller 12 comes into contact with the guide surface 18a.

  Here, the peripheral speed of the end surface of the roller 12 is the smallest in the rolling axis of the roller 12 (the center of the roller diameter) and increases toward the radially outer side. Therefore, by bringing the top of the curved surface that coincides with the center of the roller diameter into contact with the guide surface 18a, the wear of the contact portion can be effectively suppressed.

  Further, as a method for further effectively suppressing the wear of the contact portion between the end surface of the roller 12 and the guide surface 18a, the surface roughness Ra of the guide surface 18a is set to satisfy Ra <2 μm. Similarly, the surface roughness of the end face of the roller 12 is preferably within the above range.

  Further, as the output of car air conditioner compressors, automatic transmissions, manual transmissions, hybrid vehicles, and the like increases, thrust roller bearings 11 having a high load capacity are required. As a method for increasing the load capacity of the thrust roller bearing 11, for example, increasing the number of rollers 12 or increasing the effective length of the rollers 12 (indicating the length of the rolling surface) can be considered.

  However, the bearing size (inner / outer diameter, thickness, etc.) of the thrust roller bearing 11 is determined by the bearing installation space. Further, in order to increase the number of rollers 12, it is necessary to reduce the interval between adjacent pockets 17. Therefore, from the viewpoint of maintaining the rigidity of the cage 13, an easy increase in the number of rollers is not appropriate.

  Therefore, as a realistic and effective method for increasing the load capacity of the thrust roller bearing 11, there is a method of increasing the roller length. However, if the roller length of the roller 12 is increased, the end surface of the roller 12 and the end surface 17d on the radially outer side of the pocket 17 may come into contact with each other when the bearing rotates, and drilling wear may occur at the contact portion. In addition, a certain amount of clearance is required between the pocket 17 and the outer peripheral flange portion 18 due to a manufacturing problem of the cage 13 described later.

Therefore, as a means for preventing the end face of the roller 12 and the wall surface 17d on the radially outer side of the pocket 17 from coming into contact with each other, the region extending from the outer peripheral flange 18 to the pocket 17 is arranged in the radial direction of the pocket 17 from the outer peripheral flange 18. An inclined surface 17e that is linearly inclined toward the outer wall surface 17d is provided. Specifically, a flat end portion having a predetermined length is provided from the root portion of the guide surface 18a toward the radially inner side, and further gradually toward the radially outer wall surface 17d of the pocket 17 on the radially inner side. An inclined surface 17e for reducing the plate thickness is provided. By providing the inclined surface 17e, the minimum gap δ ₁ between the end surface of the roller 12 and the radially outer wall surface 17d of the pocket 17 is always in a state where δ ₁ > 0 even when the roller length of the roller 12 is increased. Can be maintained.

However, from the viewpoint of securing the rigidity of the cage 13, assuming that the thickness of the cage 13 is t ₀ and the thickness dimension of the wall surface 17 d on the radially outer side of the pocket 17 is t, t / t ₀ > 1/3 is satisfied. The inclination angle θ of the inclined surface 17e with respect to the guide surface 18a is set so as to satisfy 30 ° ≦ θ ≦ 60 °.

  Next, an example of a method for manufacturing the cage 13 having the above-described configuration will be described with reference to FIG. The cage 13 is manufactured by pressing using a steel plate such as carbon steel as a starting material.

  First, as a 1st process, the shape of the holder | retainer 13 is formed (S1). Specifically, the steel plate is punched to punch the steel plate into a disc shape, and the hole 14 is formed at the center. In addition, since the inner periphery and the outer periphery of the disc include portions that become the inner peripheral flange portion 15 and the outer peripheral flange portion 18, the external dimensions in this step are larger than the external dimensions of the finished product, and the diameter of the hole 14 Is smaller than the diameter of the finished product.

  Next, as the second step, the inner peripheral flange 15 is bent on the inner peripheral portion of the disc, the outer peripheral flange 18 is bent on the outer peripheral portion, and the roller holding portion 16 is bent between the inner peripheral flange 15 and the outer peripheral flange 18. It is formed by processing (S2). The inner peripheral flange portion 15 and the outer peripheral flange portion 18 are formed by bending the inner peripheral portion and the outer peripheral portion of the disk 90 ° to one side in the axial direction and folding the bent portion 180 ° to the other side in the axial direction. The roller holding portion 16 is bent between the inner peripheral flange portion 15 and the outer peripheral flange portion 18 so that the cross-sectional shape is substantially W-shaped.

  Next, as a third step, a plurality of pockets 17 are formed in the roller holding portion 16 (S3). Specifically, the disk is placed on a die, and the disk is punched out with a punch in the shape of a pocket 17. At this time, the pockets 17 may be processed one by one, but by processing all the pockets 17 at the same time, the processing time can be shortened and the processing accuracy can be improved.

Next, as a 4th process, the inclined surface 17e is formed in the area | region between the pocket 17 and the outer periphery collar part 18 by surface pressing (S4). Specifically, a processing jig inclined in advance at a predetermined angle so that the inclination angle θ in FIG. 3 is 30 ° ≦ θ ≦ 60 ° is pressed against the corner portion of the wall surface 17 d on the radially outer side of the pocket 17. Thus, the inclined surface 17e is formed. At this time, from the viewpoint of maintaining the rigidity of the cage 13, it is necessary to set the thickness dimension t of the wall surface 17d on the radially outer side of the pocket 17 to t / t ₀ > 1/3. The plate thickness t ₀ of the vessel 13 is 2/3 or less.

When the pocket 17 is formed, the radially outer wall surface 17d of the pocket 17 needs to be separated from the radially inner wall surface of the outer peripheral flange 18 to some extent from the viewpoint of preventing deformation of the cage 13 when the pocket is formed. There is. Specifically, the protrusion amount δ ₂ from the radially inner wall surface of the outer peripheral flange portion 18 of the radially outer wall surface 17 d of the pocket 17 needs to be about ₂₀ μm to 40 μm. The retainer 13, since to prevent contact with the radially outer wall surface 17d of the end face and the pocket 17 of the roller 12 by providing the inclined surface 17e, it is possible to secure a sufficient amount of projection [delta] _2.

  Next, as a fifth step, the guide surface 18a provided on the radially inner wall surface of the outer peripheral flange portion 18 is ground (S5), and the surface roughness Ra of the guide surface 18a is set to Ra <2 μm. . This step is not essential to achieve the object of the present invention and can be omitted. However, by setting the surface roughness Ra of the guide surface 18a within the above range, the end surface of the roller 12 and the guide surface 18a. The wear of the contact portion with can be further effectively suppressed.

  Finally, in order to obtain predetermined mechanical properties such as hardness required for the cage 13, heat treatment such as soft nitriding treatment, carburizing quenching, and tempering is performed (S6). In addition, since the processing of the cage 13 described above is performed while supplying lubricating oil to the processed portion, it is desirable to wash and dry the lubricating oil adhering to the surface of the cage 13 before the heat treatment.

  By punching the pocket 17 after the bending of the outer peripheral flange 18 as in the above manufacturing process, the processing accuracy of the pocket 17 is improved. Thereby, the roller 12 accommodated in the pocket 17 can rotate smoothly.

  In the manufacturing method of the cage 13 described above, an example of grinding is shown as a method for reducing the surface roughness of the guide surface 18a to a predetermined value or less. However, the present invention is not limited to this, and other methods may be adopted. Good. For example, barrel processing may be performed, and the gap between the punch and the die used when forming the outer peripheral flange 18 is reduced by about 2% to 3% from the plate thickness of the cage 13 for ironing. By doing so, the above-mentioned surface roughness can be realized.

  By adopting the above-described configuration, it is possible to suppress wear at the contact portion between the roller 12 and the guide surface 18a, and to reduce the amount of heat generated when the bearing rotates, so that a compressor for an car air conditioner, an automatic transmission, a manual transmission, a hybrid vehicle, etc. The thrust roller bearing 11 having excellent durability and high reliability can be obtained in the high-speed and lean lubrication environment.

  Next, a method for manufacturing the thrust roller bearing 21 and the cage 23 according to another embodiment of the present invention will be described with reference to FIGS. The basic configuration is the same as the manufacturing method of the thrust roller bearing 11 and the cage 13 shown in FIGS. 1 to 5, and thus description of common parts will be omitted, and differences will be mainly described.

First, referring to FIG. 6, the thrust roller bearing 21 includes a roller 22 and a cage 23, and the cage 23 includes an inner peripheral flange (not shown) and a roller holding portion including a plurality of pockets 27. (Not shown) and an outer peripheral flange 28 including a guide surface 28a. In the region from the outer peripheral flange portion 28 to the pocket 27, a convex curved inclined surface 27e inclined from the outer peripheral flange portion 28 toward the radially outer wall surface 27d of the pocket 27 is provided. Even when the pocket 27 is biased radially outward, the minimum gap δ ₃ between the end surface of the roller 22 and the inclined surface 27e is always set to satisfy δ ₃ > 0.

  Next, with reference to FIG. 7, in the formation process of the inclined surface 27 e in the method for manufacturing the cage 23, the angle formed between the tip surface 31 a and the surface 31 b facing the radially outer wall surface 27 d of the pocket 27 is an obtuse angle. The pocket 27 is processed by the punching tool 31 that has been used. Thus, the inclined surface 27e having a convex curved surface is formed by the surface bend generated in the radially outer wall surface 27d when the pocket is formed. That is, the pocket forming step (S3) and the inclined surface forming step (S4) shown in FIG. 5 are performed simultaneously. By adopting the above method, the inclined surface 27e can be formed simultaneously with the formation of the pocket 27, so that the number of processing steps can be reduced.

  In each of the above embodiments, the roller has shown an example in which curved surfaces bulging in the direction of the rolling axis are formed on both end faces. However, in order to obtain the effect of the present invention, the roller faces at least radially outward. It is sufficient to form a curved surface only on the end face.

  Further, in each of the above embodiments, an example is shown in which the rolling axis at the top of the curved surface formed on the end surface of the roller coincides, but the top of the curved surface has a relatively peripheral speed near the rolling axis. If it is located in a small place, the effect of the present invention can be obtained even if the two do not exactly match.

  Further, in each of the above-described embodiments, the inner peripheral collar part and the outer peripheral collar part have been folded by a predetermined length toward one side in the thickness direction of the cage, and then have been shown to be folded 180 °. The shape is not limited to this, and any shape that improves the rigidity of the cage can be used.

  Moreover, in each said embodiment, although the example which used the cage as the roller guide was shown, it is not restricted to this, The cage of a track surface guide may be sufficient.

  Further, the thrust roller bearing in each of the above embodiments is an example of a cage and roller type bearing composed of a roller and a cage. However, the present invention is not limited to this, and a bearing ring that covers one or both of the axial directions is provided. Further, it may be provided.

  Moreover, although the example which employ | adopted the cylindrical roller as a rolling element showed the thrust roller bearing in each said embodiment, this invention is applicable not only to this but a thrust needle roller bearing. Since the thrust needle roller bearing has a small thickness direction dimension, it is effective in reducing the axial dimension of the support portion.

  Furthermore, the method for manufacturing the cage in each of the above embodiments is merely a representative example, and some of the steps may be combined and performed simultaneously, or the steps may be subdivided and performed as separate steps. May be. Furthermore, other steps may be added.

  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 in thrust roller bearings that support shafts of compressors for car air conditioners, automatic transmissions, manual transmissions, and hybrid vehicles.

It is a top view of the thrust roller bearing which concerns on one Embodiment of this invention. It is sectional drawing in II-II of FIG. FIG. 3 is an enlarged view of a portion P in FIG. 1 and a portion Q in FIG. 2, and shows a state in which a roller and a guide surface are not in contact with each other. FIG. 3 is an enlarged view of a portion P in FIG. 1 and a portion Q in FIG. 2, and shows a state where rollers and a guide surface are in contact with each other. It is a flow which shows the manufacturing method of the cage for thrust roller bearings concerning one Embodiment of this invention. It is the elements on larger scale of the thrust roller bearing which concerns on other embodiment of this invention. It is a part of manufacturing method of the thrust roller bearing retainer which concerns on other embodiment of this invention, Comprising: It is a figure which shows the method of forming a pocket. It is a figure which shows the conventional thrust roller bearing.

Explanation of symbols

11, 21, 101 Thrust roller bearing, 12, 22, 102 Roller, 13, 23, 105 Cage, 105a, 105b Annular part, 105c Pocket part, 105d Outer diameter side end part, 103, 103 Race ring, 14 hole, 15 inner peripheral flange, 15a guide surface, 16 roller holding portion, 17, 27 pocket, 17a, 17b retaining portion, 17c inclined portion, 17d, 27d wall surface, 17e, 27e inclined surface, 18, 28 outer peripheral flange, 18a , 28a Guide surface, 31 Processing jig, 31a Tip surface, 31b Wall surface.

Claims (3)

A plurality of rollers having curved surfaces bulging in the direction of the rolling axis on the end surface;
A disk-shaped member having a hole formed in the center, the plurality of pockets penetrating in the thickness direction to accommodate the rollers, and located on the radially outer side of the radially outer wall surface of the pocket, the circle A cage including an outer peripheral flange extending in the axial direction along the outer periphery of the plate;
The outer peripheral flange has a guide surface that guides the end face of the roller on the radially inner wall surface,
A thrust roller bearing, wherein an inclined surface is provided in a region extending from the outer peripheral flange portion to the pocket toward the radially outer wall surface of the pocket from the outer peripheral flange portion. If the plate thickness of the cage is t ₀ and the thickness dimension of the radially outer wall surface of the pocket is t,
t / t ₀ > 1/3
The thrust roller bearing according to claim 1, wherein: The inclination angle θ of the inclined surface with respect to the guide surface is
30 ° ≦ θ ≦ 60 °
The thrust roller bearing according to claim 1 or 2, wherein

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