JP2010169141A

JP2010169141A - Thrust roller bearing

Info

Publication number: JP2010169141A
Application number: JP2009010776A
Authority: JP
Inventors: Kanji Kawasaki; 官冶川▲崎▼
Original assignee: JTEKT Corp
Current assignee: JTEKT Corp
Priority date: 2009-01-21
Filing date: 2009-01-21
Publication date: 2010-08-05

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust roller bearing capable of improving durability by protecting a retainer from damage by preventing the retainer from being between both flanges of first and second raceway rings. <P>SOLUTION: The thrust roller bearing includes a plurality of rollers 11, the retainer 20, and both first and second raceway rings 30, 40. The retainer 20 includes both annular portions 21, 22 at inner and outer diameter sides, and a plurality of pillars 24. An outer diameter side flange 31 is formed in an outer diameter end of the first raceway ring 30, and an inner diameter side flange 41 is formed in the inner diameter end of the second raceway 40. Raceway surfaces 34, 44 of the roller 11 are formed in an opposite surface of the first and second both raceway rings 30, 40. Roller guides 35, 45 are provided to be brought into contact with an end surface of the roller 11. Let a clearance dimension between both flanges 31, 41 of both first and second raceway rings and the end surface of both annular portions 21, 22 of the retainer 20 be A, and let a clearance dimension between the end surface of the roller 11 and the roller guides 35, 45 be B, a relation of A>B is set. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、オートマチックトランスミッションのトルクコンバータ、空調用圧縮機等に用いられるスラストころ軸受に関する。 The present invention relates to a thrust roller bearing used in a torque converter of an automatic transmission, a compressor for air conditioning, and the like.

従来、図５に示すように、ラストころ軸受においては、第１の軌道輪１３０の外径端に外径側鍔部１３１が形成され、第２の軌道輪１４０の内径端に内径側鍔部１４１が形成され、これら内・外径側の両鍔部１３１、１４１と、保持器１２０の内外径の両端面との間に所定の隙間Ｓが設定さた構造のものがある。
また、第１、第２の両軌道輪１３０、１４０と、複数個のころ１１１を保持した保持器１２０とを一体化するために、第１、第２の両軌道輪１３０、１４０の外径側鍔部１３１と内径側鍔部１４１に、保持器１２０の内・外径側の両端面と所定の重なり代（前記隙間Ｓよりも大きい重なり代）αをもってかしめ加工等によって抜け止め用の係止爪１３２、１４２が形成される。
そして、一体化されたスラストころ軸受は、トルクコンバータや圧縮機等のハウジング側に第１の軌道輪１３０が配置され、回転軸側に第２の軌道輪１４０が配置された状態で組み付けられる。
なお、この種のスラストころ軸受においては、例えば、特許文献１に開示されている。 Conventionally, as shown in FIG. 5, in the last roller bearing, an outer diameter side flange 131 is formed at the outer diameter end of the first bearing ring 130, and an inner diameter side flange is formed at the inner diameter end of the second race ring 140. There is a structure in which a predetermined gap S is set between both the inner and outer diameter side flanges 131 and 141 and both end surfaces of the inner and outer diameters of the cage 120.
In order to integrate the first and second race rings 130 and 140 and the cage 120 holding the plurality of rollers 111, the outer diameters of the first and second race rings 130 and 140 are integrated. The side flange 131 and the inner diameter side flange 141 have a predetermined overlap margin (overlap margin larger than the gap S) α with both end surfaces on the inner and outer diameter sides of the retainer 120 and are used for retaining by a caulking process or the like. The pawls 132 and 142 are formed.
The integrated thrust roller bearing is assembled in a state where the first bearing ring 130 is disposed on the housing side of the torque converter, the compressor, and the like, and the second bearing ring 140 is disposed on the rotating shaft side.
In addition, in this kind of thrust roller bearing, it is disclosed by patent document 1, for example.

特開２００６−２４２３５５号公報JP 2006-242355 A

ところで、トルクコンバータや圧縮機等のハウジング側と回転軸側との間に組み付けられるスラストころ軸受においては、ハウジングと回転軸とが偏心して相対回転することがあり、偏心量が大きいと、スラストころ軸受の第１、第２の両軌道輪１３０、１４０の外径側鍔部１３１と内径側鍔部１４１との間隔が広くなる部分と狭くなす部分が生じる。そして、図６に示すように、外径側鍔部１３１と内径側鍔部１４１との間隔が狭くなす部分において、外径側鍔部１３１と内径側鍔部１４１との両内側面の間に保持器１２０が挟まれ場合がある。この際、保持器１２０に径方向の圧縮荷重が作用し、この圧縮荷重によって保持器１２０が損傷される恐れがある。 By the way, in the thrust roller bearing assembled between the housing side and the rotating shaft side such as a torque converter and a compressor, the housing and the rotating shaft may be eccentrically rotated relative to each other. A portion where the distance between the outer diameter side flange 131 and the inner diameter side flange 141 of both the first and second bearing rings 130 and 140 of the bearing is widened and a portion where the distance is narrowed are generated. And as shown in FIG. 6, in the part where the space | interval of the outer diameter side collar part 131 and the inner diameter side collar part 141 becomes narrow, between both inner side surfaces of the outer diameter side collar part 131 and the inner diameter side collar part 141, The holder 120 may be pinched. At this time, a compressive load in the radial direction acts on the cage 120, and the cage 120 may be damaged by the compressive load.

この発明の目的は、前記問題点に鑑み、第１、第２の両軌道輪の外径側鍔部と内径側鍔部との両内側面の間に保持器が挟まれことがないようにし、保持器の損傷を防止して耐久性の向上を図ることができるスラストころ軸受を提供することである。 In view of the above problems, an object of the present invention is to prevent the cage from being sandwiched between the inner side surfaces of the outer diameter side collar part and the inner diameter side collar part of the first and second race rings. Another object of the present invention is to provide a thrust roller bearing capable of preventing the cage from being damaged and improving the durability.

前記課題を解決するために、この発明の請求項１に係るスラストころ軸受は、複数個のころと、保持器と、第１、第２の両軌道輪とを備えたスラストころ軸受であって、
前記保持器は、径方向に所定間隔を隔てる内・外径側の両環状部と、これら両環状部を連結すると共に、前記ころを転動可能に保持するポケットを区画形成する複数の柱部とを備え、
前記第１の軌道輪の外径端には外径側鍔部が形成され、前記第２の軌道輪の内径端には内径側鍔部が形成され、
前記第１、第２の両軌道輪の対向面には、前記ころが転動可能な軌道面が形成されると共に、これら軌道面に隣接して前記ころの端面に当接可能なころ案内部を有する凸部が設けられ、
前記第１、第２の両軌道輪の内・外径側の両鍔部と前記保持器の内・外径側の両環状部の端面との間の隙間寸法をＡとし、前記ころの端面と前記ころ案内部との間の隙間寸法をＢとしたときに、Ａ＞Ｂの関係となるように設定されていることを特徴とする。 In order to solve the above problems, a thrust roller bearing according to a first aspect of the present invention is a thrust roller bearing comprising a plurality of rollers, a cage, and both first and second race rings. ,
The retainer has a plurality of pillar portions that divide and form both inner and outer diameter side annular portions that are spaced apart from each other in the radial direction and pockets that hold the rollers in a rollable manner. And
An outer diameter side flange is formed at the outer diameter end of the first race ring, and an inner diameter side flange is formed at the inner diameter end of the second race ring,
Roller guide portions capable of rolling the rollers are formed on opposing surfaces of the first and second race rings, and roller guide portions that can contact the end surfaces of the rollers adjacent to the race surfaces. A convex portion having
The clearance between the inner and outer diameter side flanges of the first and second races and the end faces of the inner and outer diameter side annular portions of the cage is A, and the end surface of the roller When the clearance dimension between the roller guide portion and the roller guide portion is B, the relationship is set such that A> B.

前記構成によると、トルクコンバータや圧縮機等のハウジング側に第１の軌道輪が配置され、回転軸側に第２の軌道輪が配置された状態において、ハウジングと回転軸とが偏心して相対回転する際に、第１、第２の両軌道輪の内径側鍔部と外径側鍔部との間隔が広くなる部分と狭くなす部分が生じる。そして、内径側鍔部と外径側鍔部との間隔が狭くなる部分において、第１、第２の両軌道輪の対向面に形成された両ころ案内部の間にころが挟まれる。
すなわち、ハウジングと回転軸との偏心による圧縮荷重がころによって受けられる。この結果、第１、第２の両軌道輪の内径側鍔部と外径側鍔部との両内側面の間に保持器が挟まれことを解消することができ、保持器の損傷を防止して耐久性の向上を図ることができる。 According to the above configuration, in the state where the first race ring is arranged on the housing side of the torque converter, the compressor, etc., and the second race ring is arranged on the rotary shaft side, the housing and the rotary shaft are decentered and relatively rotated. In doing so, a portion where the distance between the inner diameter side collar portion and the outer diameter side collar portion of both the first and second bearing rings is widened and a narrow portion are generated. And in the part where the space | interval of an inner diameter side collar part and an outer diameter side collar part becomes narrow, a roller is pinched | interposed between the roller guide parts formed in the opposing surface of both the 1st and 2nd track rings.
That is, a compressive load due to the eccentricity of the housing and the rotating shaft is received by the rollers. As a result, it is possible to eliminate the cage from being sandwiched between the inner side surfaces of the inner diameter side collar portion and the outer diameter side collar portion of both the first and second race rings, thereby preventing the cage from being damaged. As a result, durability can be improved.

請求項２に係るスラストころ軸受は、請求項１に記載のスラストころ軸受であって、
第１、第２の両軌道輪の対向面は段差面に形成され、低い面を軌道面とし、高い面を凸部とすると共に、前記凸部の側面をころ案内部としていることを特徴とする。 The thrust roller bearing according to claim 2 is the thrust roller bearing according to claim 1,
The opposing surfaces of the first and second races are formed as stepped surfaces, the lower surface is a raceway surface, the higher surface is a convex portion, and the side surface of the convex portion is a roller guide portion. To do.

前記構成によると、第１、第２の両軌道輪の対向面を段差面に形成することによって、軌道面ところ案内部とを容易に形成することができる。 According to the said structure, a track surface and a guide part can be easily formed by forming the opposing surface of both the 1st and 2nd track rings in a level | step difference surface.

この発明の実施例１に係るスラストころ軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows the thrust roller bearing which concerns on Example 1 of this invention. 同じくスラストころ軸受の第１、第２の両軌道輪と、ころと、保持器との関係を示す縦断面図である。It is a longitudinal cross-sectional view which similarly shows the relationship between the 1st, 2nd both bearing rings of a thrust roller bearing, a roller, and a holder | retainer. 同じく第１、第２の両軌道輪のころ案内部の間にころが挟まれた状態を示す説明図である。It is explanatory drawing which shows the state by which the roller was similarly pinched | interposed between the roller guide parts of both the 1st and 2nd track rings. 保持器の向きを表裏逆にして第１、第２の両軌道輪の間に配設した実施態様を示す説明図である。It is explanatory drawing which shows the embodiment arrange | positioned between the 1st, 2nd track rings, with the direction of a holder | retainer turned upside down. 従来のスラストころ軸受の第１、第２の両軌道輪と、ころと、保持器との関係を示す縦断面図である。It is a longitudinal cross-sectional view which shows the relationship between the 1st, 2nd both bearing rings of a conventional thrust roller bearing, a roller, and a holder | retainer. 同じく第１、第２の両軌道輪の内外径の両鍔部の間に保持器が挟まれた状態を示す説明図である。It is explanatory drawing which shows the state by which the holder | retainer was similarly pinched | interposed between both the collar parts of the inner and outer diameter of both 1st and 2nd track rings.

この発明を実施するための最良の形態について実施例にしたがって説明する。 The best mode for carrying out the present invention will be described in accordance with an embodiment.

この発明の実施例１を図１〜図３にしたがって説明する。
図１はこの発明の実施例１に係るスラストころ軸受を示す縦断面図である。図２はスラストころ軸受の第１、第２の両軌道輪と、ころと、保持器との関係を示す縦断面図である。図３は第１、第２の両軌道輪のころ案内部の間にころが挟まれた状態を示す説明図である。 A first embodiment of the present invention will be described with reference to FIGS.
1 is a longitudinal sectional view showing a thrust roller bearing according to Embodiment 1 of the present invention. FIG. 2 is a longitudinal sectional view showing the relationship between the first and second bearing rings of the thrust roller bearing, the rollers, and the cage. FIG. 3 is an explanatory view showing a state in which the rollers are sandwiched between the roller guide portions of the first and second track rings.

図１に示すように、トルクコンバータや圧縮機等のハウジング１側と回転軸５側との間に組み付けられるスラストころ軸受１０は、複数個のころ１１と、保持器２０と、第１、第２の両軌道輪３０、４０とを備えている。
図２に示すように、保持器２０は、径方向に所定間隔を隔てる内・外径側の両環状部２１、２２と、これら両環状部２１、２２を連結すると共に、複数のころ１１を転動可能に保持するポケット２３を区画形成する複数の柱部２４とを備えている。
複数の柱部２４は、縦断面略Ｍ型状をなし、第１の軌道輪３０の軌道面３４に接近して突出する径方向中間部２５と、第２の軌道輪４０の軌道面４４に接近して突出する径方向両側部２７と、これら径方向中間部２５と径方向両側部２７とを連結する傾斜連結部２６とを備えている。さらに、径方向両側部２７は傾斜連結部２８をもって内・外径側の両環状部２１、２２に連結されている。
なお、複数の柱部２４の径方向中間部２５及び径方向両側部２７の対向面には、ころ１１を抜け止めするための抜止爪（図示しない）が形成されている。 As shown in FIG. 1, a thrust roller bearing 10 assembled between the housing 1 side and the rotating shaft 5 side of a torque converter, a compressor, or the like includes a plurality of rollers 11, a cage 20, first, first Two race rings 30 and 40 are provided.
As shown in FIG. 2, the retainer 20 connects the inner and outer diameter side annular portions 21 and 22 that are spaced apart from each other by a predetermined distance in the radial direction, and connects the annular portions 21 and 22 together with the plurality of rollers 11. And a plurality of pillars 24 that define and form a pocket 23 that can be rolled.
The plurality of column portions 24 have a substantially M-shaped vertical cross section, and are formed on the radial intermediate portion 25 that protrudes close to the raceway surface 34 of the first raceway ring 30 and the raceway surface 44 of the second raceway ring 40. Both side portions 27 in the radial direction projecting close to each other, and inclined connection portions 26 that connect the intermediate portions 25 in the radial direction and both side portions 27 in the radial direction are provided. Further, both radial side portions 27 are connected to both the inner and outer diameter side annular portions 21 and 22 with inclined connecting portions 28.
Note that retaining claws (not shown) for retaining the rollers 11 are formed on the opposing surfaces of the radial intermediate portions 25 and the radial side portions 27 of the plurality of column portions 24.

図１と図２に示すように、ハウジング側に配置される第１の軌道輪３０の外径端には、ハウジング１の組み付け孔２に嵌込まれる外径側鍔部３１が形成されている。
また、回転軸５側に配置される第２の軌道輪４０の内径端には、回転軸５の外周に嵌挿される内径側鍔部４１が形成されている。
また、第１、第２の両軌道輪３０、４０と、複数個のころ１１を保持した保持器２０とを一体化するために、第１の軌道輪３０の外径側鍔部３１と、第２の軌道輪４０の内径側鍔部４１の各先端部の周方向の複数箇所には、保持器２０の内・外径側の両環状部２１、２２端面とが所定の重なり代をもって抜け止め用の各複数の係止爪３２、４２がかしめ加工等によって形成されている。 As shown in FIGS. 1 and 2, an outer diameter side flange portion 31 that is fitted into the assembly hole 2 of the housing 1 is formed at the outer diameter end of the first race 30 disposed on the housing side. .
In addition, an inner diameter side flange 41 that is fitted to the outer periphery of the rotation shaft 5 is formed at the inner diameter end of the second race ring 40 disposed on the rotation shaft 5 side.
In order to integrate both the first and second race rings 30 and 40 and the cage 20 holding the plurality of rollers 11, the outer diameter side flange 31 of the first race ring 30, The annular surfaces 21 and 22 on both the inner and outer diameter sides of the retainer 20 are removed with a predetermined overlap margin at a plurality of positions in the circumferential direction of the respective distal end portions of the inner diameter side flange 41 of the second race ring 40. A plurality of locking claws 32 and 42 for locking are formed by caulking or the like.

図２に示すように、第１、第２の両軌道輪３０、４０の対向面には、ころ１１が転動可能な軌道面３４、４４がそれぞれ形成されると共に、これら軌道面３４、４４にそれぞれ隣接してころ１１の両端面に当接可能なころ案内部３５、４５を有する凸部３６、４６が設けられている。
この実施例１において、第１、第２の両軌道輪３０、４０の対向面は段差面に形成され、低い面を軌道面３４、４４とし、高い面を凸部３６、４６としている。そして、各凸部３６、４６の側面（軌道面３４、４４との境界部側面）をころ案内部３６、４６としている。 As shown in FIG. 2, raceway surfaces 34 and 44 on which the rollers 11 can roll are formed on the opposing surfaces of the first and second raceways 30 and 40, respectively. Convex portions 36 and 46 having roller guide portions 35 and 45 that can be in contact with both end surfaces of the roller 11 are provided adjacent to each other.
In the first embodiment, the opposing surfaces of the first and second race rings 30 and 40 are formed as stepped surfaces, with the lower surfaces being the race surfaces 34 and 44 and the higher surfaces being the convex portions 36 and 46. The side surfaces of the convex portions 36 and 46 (side surfaces of the boundary portions with the raceway surfaces 34 and 44) serve as roller guide portions 36 and 46, respectively.

図２に示すように、第１、第２の両軌道輪３０、４０の内・外径側の両鍔部３１、４１と保持器２０の内・外径側の両環状部２１、２２の端面との間の隙間寸法をＡとし、ころ１１の両端面ところ案内部３６、４６との間の隙間寸法をＢとしたときに、Ａ＞Ｂの関係となるように設定されている。 As shown in FIG. 2, both the inner and outer diameter side flanges 31 and 41 of both the first and second race rings 30 and 40 and the inner and outer diameter side annular portions 21 and 22 of the cage 20. When the clearance dimension between the end faces is A and the clearance dimension between the both end faces of the roller 11 and the guide portions 36 and 46 is B, the relationship is set such that A> B.

また、図２に示すように、第２の軌道輪４０の内径側鍔部４１と保持器２０の内径側環状部２１の端面との間の隙間寸法をＡとし、第２の軌道輪４０のころ案内部４６と保持器２０の柱部２４の径方向両側部２７の片側部分との間の隙間寸法をＣとしたときに、Ａ＜Ｃの関係となるように設定されることが好ましい。
Ａ＜Ｃの関係となるように設定した場合には、第１の軌道輪３０の外径側鍔部３１と、第２の軌道輪４０の内径側鍔部４１との間隔が狭くなる方向に、これら第１、第２の両軌道輪３０が変位したときでも、保持器２０の柱部２４の径方向両側部２７の片側部分（エッジ部分）がころ案内部４６に当接（接触）することがない。このため、第１の軌道輪３０の軌道面３４と、第２の軌道輪４０の凸部４６との間に保持器２０が挟まれて拘束されることがない。 Further, as shown in FIG. 2, the clearance dimension between the inner diameter side flange 41 of the second bearing ring 40 and the end surface of the inner diameter side annular part 21 of the cage 20 is A, and the second bearing ring 40 It is preferable that the relationship of A <C is established, where C is the size of the gap between the roller guide portion 46 and one side portion of the radial side portions 27 of the column portion 24 of the cage 20.
In the case where the relationship of A <C is set, the distance between the outer diameter side flange 31 of the first race 30 and the inner diameter 41 of the second race 40 becomes narrower. Even when both the first and second race rings 30 are displaced, one side portion (edge portion) of each of the radial side portions 27 of the column portion 24 of the cage 20 abuts (contacts) the roller guide portion 46. There is nothing. For this reason, the cage 20 is not sandwiched and restrained between the raceway surface 34 of the first raceway ring 30 and the convex portion 46 of the second raceway ring 40.

この実施例１に係るスラストころ軸受は上述したように構成される。
したがって、図１に示すように、トルクコンバータや圧縮機等のハウジング１側に第１の軌道輪３０が配置され、回転軸５側に第２の軌道輪４０が配置された状態で組み付けられる。この組み付け状態において、ハウジング１と回転軸５とが偏心して相対回転すると、スラストころ軸受１０では、第１の軌道輪３０の外径側鍔部３１と、第２の軌道輪４０の内径側鍔部４１との間隔が広くなる部分と狭くなす部分が生じる。
この際に、図３に示すように、第１の軌道輪３０の外径側鍔部３１と、第２の軌道輪４０の内径側鍔部４１との間隔が狭くなる部分において、これら第１、第２の両軌道輪３０、４０の対向面に形成された両ころ案内部３５、４５にころ１１の両端面が当接してこれら両ころ案内部３５、４５の間にころ１１が挟まれる。
これによって、ハウジング１と回転軸５との偏心による圧縮荷重がころ１１によって受けられる。この結果、第１の軌道輪３０の外径側鍔部３１と、第２の軌道輪４０の内径側鍔部４１との両内側面の間に保持器２０が挟まれことを解消することができ、保持器２０の損傷を防止して耐久性の向上を図ることができる。 The thrust roller bearing according to the first embodiment is configured as described above.
Therefore, as shown in FIG. 1, the first bearing ring 30 is arranged on the housing 1 side such as a torque converter or a compressor, and the second bearing ring 40 is arranged on the rotating shaft 5 side. In this assembled state, when the housing 1 and the rotary shaft 5 are eccentrically rotated relative to each other, in the thrust roller bearing 10, the outer diameter side flange 31 of the first bearing ring 30 and the inner diameter side flange of the second bearing ring 40. The part where the space | interval with the part 41 becomes wide and the part which narrows arise.
At this time, as shown in FIG. 3, in the portion where the distance between the outer diameter side flange 31 of the first race 30 and the inner diameter 41 of the second race 40 becomes narrow, these first The both end surfaces of the roller 11 come into contact with both roller guide portions 35 and 45 formed on the opposing surfaces of the second both race rings 30 and 40, and the roller 11 is sandwiched between these roller guide portions 35 and 45. .
As a result, the roller 11 receives a compressive load due to the eccentricity of the housing 1 and the rotating shaft 5. As a result, it is possible to eliminate the cage 20 being sandwiched between the inner side surfaces of the outer diameter side flange 31 of the first race 30 and the inner diameter side flange 41 of the second race 40. It is possible to prevent the cage 20 from being damaged and to improve the durability.

なお、この発明は前記実施例１に限定するものではなく、この発明の要旨を逸脱しない範囲内において、種々なる形態で実施することもできる。
例えば、前記実施例１においては、図２に示すように、第１、第２の両軌道輪３０、４０の対向面を段差面に形成することによって、軌道面３４、４４と、ころ案内部３５、４５とを容易に形成するようにしたが、第１、第２の両軌道輪３０、４０とは別部材、例えば、環状部材等を第１、第２の両軌道輪３０、４０の所定位置に取り付けて、この環状部材の一側面をころ案内部としてもこの発明を実施可能である。
また、前記実施例１においては、保持器２０の柱部２４の径方向中間部２５が第１軌道輪３０の軌道面３４に接近し、径方向両側部２７が第２の軌道輪４０の軌道面４４に接近する状態で配置したが、図４に示すように、保持器２０の柱部２４の径方向中間部２５が第２軌道輪４０の軌道面４４に接近し、径方向両側部２７が第１の軌道輪３０の軌道面３４に接近する状態で配置してもよい。
この場合、第１の軌道輪３０の内径側鍔部３１と保持器２０の外径側環状部２２の端面との間の隙間寸法をＡ’とし、第１の軌道輪３０のころ案内部３６と保持器２０の柱部２４の径方向両側部２７の片側部分との間の隙間寸法をＣ’としたときに、Ａ’＜Ｃ’の関係となるように設定されることが好ましい。 In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can also be implemented with a various form.
For example, in the first embodiment, as shown in FIG. 2, the opposing surfaces of the first and second race rings 30 and 40 are formed on the stepped surface, so that the raceway surfaces 34 and 44 and the roller guide portion are formed. 35 and 45 are formed easily, but a member different from the first and second race rings 30 and 40, for example, an annular member or the like is used for the first and second race rings 30 and 40. The present invention can also be implemented by attaching it to a predetermined position and using one side surface of the annular member as a roller guide.
Further, in the first embodiment, the radial intermediate portion 25 of the column portion 24 of the cage 20 approaches the raceway surface 34 of the first raceway ring 30, and both radial side portions 27 are raceways of the second raceway ring 40. Although arranged so as to approach the surface 44, as shown in FIG. 4, the radial intermediate portion 25 of the pillar portion 24 of the cage 20 approaches the raceway surface 44 of the second race ring 40, and both radial side portions 27. May be arranged in a state of approaching the raceway surface 34 of the first race 30.
In this case, the clearance dimension between the inner diameter side flange portion 31 of the first race ring 30 and the end face of the outer diameter side annular portion 22 of the cage 20 is A ′, and the roller guide portion 36 of the first race ring 30. It is preferable that the relationship between A ′ <C ′ is established, where C ′ is a gap dimension between the one side portion of the both side portions 27 in the radial direction of the column portion 24 of the cage 20.

１０スラストころ軸受
１１ころ
２０保持器
２１内径側環状部
２２外径側環状部
２３ポケット
２４柱部
３０第１の軌道輪
３１外径側鍔部
３４軌道面
３５ころ案内部
３６凸部
４０第２の軌道輪
４１外径側鍔部
４４軌道面
４５ころ案内部
４６凸部 DESCRIPTION OF SYMBOLS 10 Thrust roller bearing 11 Roller 20 Cage 21 Inner diameter side annular part 22 Outer diameter side annular part 23 Pocket 24 Column part 30 First race ring 31 Outer diameter side collar part 34 Race surface 35 Roller guide part 36 Convex part 40 Second Bearing ring 41 outer diameter side flange 44 raceway surface 45 roller guide portion 46 convex portion

Claims

A thrust roller bearing comprising a plurality of rollers, a cage, and both first and second bearing rings,
The retainer has a plurality of pillar portions that divide and form both inner and outer diameter side annular portions that are spaced apart from each other in the radial direction and pockets that hold the rollers in a rollable manner. And
An outer diameter side flange is formed at the outer diameter end of the first race ring, and an inner diameter side flange is formed at the inner diameter end of the second race ring,
Roller guide portions capable of rolling the rollers are formed on opposing surfaces of the first and second race rings, and roller guide portions that can contact the end surfaces of the rollers adjacent to the race surfaces. A convex portion having
The clearance between the inner and outer diameter side flanges of the first and second races and the end faces of the inner and outer diameter side annular portions of the cage is A, and the end surface of the roller A thrust roller bearing, which is set to have a relationship of A> B, where B is a clearance dimension between the roller guide portion and the roller guide portion.

The thrust roller bearing according to claim 1,
The opposing surfaces of the first and second races are formed as stepped surfaces, the lower surface is a raceway surface, the higher surface is a convex portion, and the side surface of the convex portion is a roller guide portion. Thrust roller bearing.