JP5397505B2 - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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JP5397505B2
JP5397505B2 JP2012129070A JP2012129070A JP5397505B2 JP 5397505 B2 JP5397505 B2 JP 5397505B2 JP 2012129070 A JP2012129070 A JP 2012129070A JP 2012129070 A JP2012129070 A JP 2012129070A JP 5397505 B2 JP5397505 B2 JP 5397505B2
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tapered roller
peripheral surface
roller bearing
diameter
column
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JP2012163217A (en
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亮輔 山田
智治 齋藤
匠 竹内
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring

Description

本発明は、油潤滑で使用される円すいころ軸受に関し、より詳細には、自動車用トランスミッション又は自動車用でデファレンシャルギヤに使用される円すいころ軸受に関する。   The present invention relates to a tapered roller bearing used in oil lubrication, and more particularly, to a tapered roller bearing used in a transmission for an automobile or a differential gear in an automobile.

円すいころ軸受は、大きなラジアル荷重およびアキシャル荷重を支持して高速回転での使用が可能であり、且つコンパクトであるため、トランスミッション、デファレンシャルギヤなど、自動車の減速装置部分などに多用されている。このような円すいころ軸受では、軸受の回転に伴うポンプ作用によって、潤滑油が内輪の小鍔部と保持器の小径環状部側端部との間から流入し、内輪の大鍔部と保持器の大径環状部側端部との間から流出するように構成されている。   Tapered roller bearings can be used at high speed rotation while supporting large radial loads and axial loads, and are compact, so they are frequently used in parts such as transmissions, differential gears, and other vehicle speed reducers. In such a tapered roller bearing, the lubricating oil flows in between the small ring portion of the inner ring and the small diameter annular portion side end of the cage due to the pump action accompanying the rotation of the bearing, and the large ring portion of the inner ring and the cage It is comprised so that it may flow out from between the large diameter annular part side edge parts.

一方、円すいころ軸受の回転トルクは、円すいころと内輪との摩擦抵抗や、軸受内部に滞留する潤滑油の攪拌抵抗が主な要因となって発生し、特に、高速回転領域で使用される円すいころ軸受においては、潤滑油の攪拌抵抗が大きな要因となっている。自動車の減速装置部分などで用いられる場合、潤滑油の供給量が多く、そのため潤滑油の攪拌抵抗が大きくなりやすいという問題がある。   On the other hand, the rotational torque of tapered roller bearings is mainly caused by the frictional resistance between the tapered rollers and the inner ring and the stirring resistance of the lubricating oil that stays inside the bearing. In roller bearings, the agitation resistance of lubricating oil is a major factor. When used in a reduction gear part of an automobile, etc., there is a problem that the supply amount of lubricating oil is large, so that the stirring resistance of the lubricating oil tends to increase.

図１２に示すように、特許文献１に記載の円すいころ軸受１００では、プレス成形された金属製保持器１０１の内径端面１０１ａと、内輪１０２の小径側端部１０２ａの外周面１０２ｂの隙間を小さくしてラビリンスシールを形成し、流入する潤滑油量の低減を図ることにより、攪拌トルクを低減することが提案されている。   As shown in FIG. 12, in the tapered roller bearing 100 described in Patent Document 1, the gap between the inner diameter end surface 101a of the press-molded metal cage 101 and the outer peripheral surface 102b of the smaller diameter side end portion 102a of the inner ring 102 is reduced. Thus, it has been proposed to reduce the stirring torque by forming a labyrinth seal and reducing the amount of lubricating oil flowing in.

特開２００５−６９４２１号公報JP 2005-69421 A

しかしながら、特許文献１に記載の円すいころ軸受１００は、軸受への潤滑油流入量の低減を図ることにより攪拌トルクの低減を図っているが、高速回転時にはころ１０３の回転によりエアーカーテンが発生し、潤滑油の軸受内への進入を妨げるため内輪１０２の小鍔部外周面１０２ｃと保持器１０１のかしめ部１０１ｂとの隙間Ａに潤滑油が滞留しやすく、その結果、円すいころ軸受１００の攪拌トルクが上昇しやすいという問題があった。   However, the tapered roller bearing 100 described in Patent Document 1 reduces the agitation torque by reducing the amount of lubricating oil flowing into the bearing, but an air curtain is generated by the rotation of the roller 103 during high-speed rotation. In order to prevent the lubricating oil from entering the bearing, the lubricating oil tends to stay in the gap A between the outer peripheral surface 102c of the small collar portion 102c of the inner ring 102 and the caulking portion 101b of the retainer 101. As a result, the tapered roller bearing 100 is agitated. There was a problem that the torque was likely to rise.

本発明は、前述した課題に鑑みてなされたものであり、その目的は、潤滑油の排出効果を高めて軸受内部に滞留する潤滑油量を減少させて、攪拌トルクを低減することができる円すいころ軸受を提供することにある。   The present invention has been made in view of the above-described problems, and an object of the present invention is to increase the lubricating oil discharge effect and reduce the amount of lubricating oil staying in the bearing, thereby reducing the stirring torque. It is to provide a roller bearing.

本発明の上記目的は、下記の構成により達成される。
（１） 内輪と、外輪と、前記内輪と前記外輪の間を周方向に転動可能な複数の円すいころと、前記複数の円すいころを所定の間隔で保持する樹脂製保持器とを備え、油潤滑で使用される円すいころ軸受であって、
保持器柱部は、小径側における柱部内周面の回転軸に対する傾きが、大径側における柱部内周面の回転軸に対する傾きより大きく、軸受内部の潤滑油の排出を促進する円弧部を備え、
前記保持器柱部は前記保持器の小径環状部と大径環状部を連接し、
前記保持器の前記小径環状部は、内周面が前記内輪の小鍔部の外周面に対向してラビリンスシールを構成し、
前記柱部の最内径部は前記小鍔部の外周面よりも内径側に位置し、
前記大径環状部の内周面は、前記円すいころのピッチ円直径より外径側に位置することを特徴とする円すいころ軸受。
（２） 前記円弧部は、前記柱部の前記最内径部に連なっていることを特徴とする（１）に記載の円すいころ軸受。
（３） 前記円弧部の外径側端部は、前記円すいころのピッチ円直径より外径側に位置することを特徴とする（１）又は（２）に記載の円すいころ軸受。
（４） 前記柱部内周面が略直線状に形成され前記柱部内周面の傾きが柱部外周面の傾きと同一に形成された平行部を備え、
前記平行部は、前記円弧部の外径側端部から連続して形成されることを特徴とする（１）〜（３）のいずれかに記載の円すいころ軸受。 The above object of the present invention can be achieved by the following constitution.
(1) An inner ring, an outer ring, a plurality of tapered rollers capable of rolling in a circumferential direction between the inner ring and the outer ring, and a resin cage that holds the plurality of tapered rollers at a predetermined interval, Tapered roller bearings used in oil lubrication,
The cage column portion has an arc portion that has an inclination with respect to the rotation axis of the inner circumferential surface of the column portion on the small diameter side that is larger than an inclination with respect to the rotation axis of the inner circumferential surface of the column portion on the large diameter side, and promotes discharge of lubricating oil inside the bearing. ,
The retainer column portion connects the small diameter annular portion and the large diameter annular portion of the retainer,
The small-diameter annular portion of the cage constitutes a labyrinth seal with an inner peripheral surface facing an outer peripheral surface of the small collar portion of the inner ring,
The innermost diameter part of the column part is located on the inner diameter side of the outer peripheral surface of the small collar part,
A tapered roller bearing , wherein an inner peripheral surface of the large-diameter annular portion is located on an outer diameter side with respect to a pitch circle diameter of the tapered roller.
(2) The tapered roller bearing according to (1), wherein the arc portion is continuous with the innermost diameter portion of the column portion.
( 3 ) The tapered roller bearing according to (1) or (2) , wherein an outer diameter side end portion of the arc portion is located on an outer diameter side with respect to a pitch circle diameter of the tapered roller .
( 4) The columnar inner peripheral surface is formed in a substantially linear shape, and the columnar inner peripheral surface has a parallel portion formed with the same inclination as the columnar outer peripheral surface,
The tapered roller bearing according to any one of (1) to (3), wherein the parallel portion is formed continuously from an outer diameter side end portion of the arc portion .

本発明の円すいころ軸受によれば、保持器柱部が、小径側における柱部内周面の回転軸に対する傾きを大径側における保持器内周面の回転軸に対する傾きより大きい円弧部を備えたことにより、潤滑油が大径側に流れやすくなる。これにより、潤滑油の排出効果が高まり軸受内部に滞留する潤滑油量が減少し、攪拌トルクを低減することができる。   According to the tapered roller bearing of the present invention, the retainer column portion has an arc portion whose inclination with respect to the rotation axis of the column inner peripheral surface on the small diameter side is larger than the inclination with respect to the rotation axis of the retainer inner peripheral surface on the large diameter side. As a result, the lubricating oil easily flows to the large diameter side. Thereby, the draining effect of the lubricating oil is enhanced, the amount of the lubricating oil staying inside the bearing is reduced, and the stirring torque can be reduced.

本発明の第１実施形態である円すいころ軸受の軸方向断面図である。It is an axial sectional view of the tapered roller bearing which is the first embodiment of the present invention. 図１に示す保持器の全体斜視図である。It is a whole perspective view of the holder | retainer shown in FIG. 図１に示す保持器の要部斜視図である。It is a principal part perspective view of the holder | retainer shown in FIG. 図１のＡ−Ａ線矢視図であり、第１実施形態である円すいころ軸受の径方向断面図である。It is an AA arrow directional view of Drawing 1, and is a radial direction sectional view of a tapered roller bearing which is a 1st embodiment. 図１に示す保持器における潤滑油の流れ方向を説明する要部断面図である。It is principal part sectional drawing explaining the flow direction of the lubricating oil in the holder | retainer shown in FIG. 第２実施形態の円すいころ軸受に組み込まれる保持器の断面図である。It is sectional drawing of the holder | retainer integrated in the tapered roller bearing of 2nd Embodiment. 第３実施形態の円すいころ軸受に組み込まれる保持器の断面図である。It is sectional drawing of the holder | retainer integrated in the tapered roller bearing of 3rd Embodiment. 第４実施形態の円すいころ軸受に組み込まれる保持器の断面図である。It is sectional drawing of the holder | retainer integrated in the tapered roller bearing of 4th Embodiment. 第５実施形態の円すいころ軸受に組み込まれる保持器の断面図である。It is sectional drawing of the holder | retainer integrated in the tapered roller bearing of 5th Embodiment. 図１のＡ−Ａ線矢視図であり、第６実施形態の円すいころ軸受の径方向断面図である。It is an AA arrow directional view of FIG. 1, and is radial direction sectional drawing of the tapered roller bearing of 6th Embodiment. 第７実施形態の円すいころ軸受の径方向断面図である。It is radial direction sectional drawing of the tapered roller bearing of 7th Embodiment. 従来の円すいころ軸受の軸方向断面図である。It is an axial sectional view of a conventional tapered roller bearing.

以下、本発明に係る円すいころ軸受の各実施形態を図面に基づいて詳細に説明する。   Hereinafter, each embodiment of the tapered roller bearing according to the present invention will be described in detail with reference to the drawings.

＜第１実施形態＞
まず、図１〜図５を参照して、本発明に係る円すいころ軸受の第１実施形態について説明する。
図１に示すように、本実施形態の円すいころ軸受１は、外周面に内輪軌道面２ａが形成された内輪２と、内周面に外輪軌道面３ａが形成された外輪３と、内輪軌道面２ａと外輪軌道面３ａ間を周方向に転動可能な複数の円すいころ４と、複数の円すいころ４を所定の間隔で転動可能に保持する保持器５とを備えている。 <First Embodiment>
First, with reference to FIGS. 1-5, 1st Embodiment of the tapered roller bearing which concerns on this invention is described.
As shown in FIG. 1, the tapered roller bearing 1 of this embodiment includes an inner ring 2 having an inner ring raceway surface 2a formed on the outer peripheral surface, an outer ring 3 having an outer ring raceway surface 3a formed on the inner peripheral surface, and an inner ring raceway. A plurality of tapered rollers 4 capable of rolling in the circumferential direction between the surface 2a and the outer ring raceway surface 3a, and a cage 5 that holds the plurality of tapered rollers 4 so as to be capable of rolling at a predetermined interval are provided.

内輪２は、内輪軌道面２ａと、その小径側端部に半径方向外方に突出して形成された小鍔部２ｂと、大径側端部に半径方向外方に突出して形成された大鍔部２ｃとを備え、内輪軌道面２ａは、内輪２の外周面が小鍔部２ｂから大鍔部２ｃに向うに従って、外径が次第に大きくなるように形成されている。   The inner ring 2 includes an inner ring raceway surface 2a, a small flange portion 2b formed to protrude radially outward at an end portion on the small diameter side, and a large rod formed to protrude radially outward at an end portion on the large diameter side. The inner ring raceway surface 2a is formed such that the outer diameter gradually increases as the outer peripheral surface of the inner ring 2 moves from the small flange portion 2b to the large flange portion 2c.

外輪３は、外輪軌道面２ｂが外輪３の内周面に小径側から大径側に向けて内径が次第に大きくなるように形成されている。   The outer ring 3 is formed so that the outer ring raceway surface 2b gradually increases in diameter from the small diameter side to the large diameter side on the inner peripheral surface of the outer ring 3.

保持器５は、例えば図２に示すように、小径環状部６と、大径環状部７と、小径環状部６と大径環状部７とを連結して周方向に略等間隔で配置される複数の柱部８とを備え、これら小径環状部６、大径環状部７、および隣接する柱部８とで円すいころ４を保持するポケット９を構成する。   For example, as shown in FIG. 2, the cage 5 is arranged at substantially equal intervals in the circumferential direction by connecting the small-diameter annular portion 6, the large-diameter annular portion 7, and the small-diameter annular portion 6 and the large-diameter annular portion 7. A plurality of column portions 8 are provided, and the small diameter annular portion 6, the large diameter annular portion 7, and the adjacent column portion 8 constitute a pocket 9 that holds the tapered roller 4.

保持器５の小径環状部６は、その内周面が内輪２の小鍔部２ｂと略平行に近接して対向配置され、小径環状部６の内周面６ａと小鍔部２ｂの外周面とによってラビリンスシール部１１が形成されている。   The inner peripheral surface of the small-diameter annular portion 6 of the cage 5 is disposed so as to face the small collar portion 2b of the inner ring 2 in a substantially parallel manner, and the inner peripheral surface 6a of the small-diameter annular portion 6 and the outer peripheral surface of the small collar portion 2b. Thus, the labyrinth seal portion 11 is formed.

保持器５の柱部８は、例えば図３、図４に示すように、小径環状部６と大径環状部７とを連接する柱部本体２０と、柱部本体２０から径方向内側に向けて突出して形成される凸部３０を有する。柱部本体２０は、円周方向両側面に径方向内方に向けて僅かに幅狭となる側面２０ｂを有し、柱部本体２０の内周面からはさらに径方向内方に向けて幅狭となる凸部外径部３１と、凸部外径部３１から一様の幅で内輪２の小鍔部２ｂより内径側であって内輪軌道面２ａ近傍まで延びる凸部内径部３２が形成されている。この凸部外径部３１と凸部内径部３２とから凸部３０が構成されている。
なお、保持器５は、凸部外径部３１の側面３１ｂがころ案内面となって円すいころ４に当接することにより周方向の位置決めがなされ、回転時には円すいころ４により案内される。 As shown in FIGS. 3 and 4, for example, as shown in FIGS. 3 and 4, the retainer 5 has a pillar body 20 that connects the small-diameter annular part 6 and the large-diameter annular part 7, and a radially inward direction from the pillar part body 20. And has a convex portion 30 that protrudes. The column main body 20 has side surfaces 20b that are slightly narrower inward in the radial direction on both side surfaces in the circumferential direction, and further extends inward in the radial direction from the inner peripheral surface of the column main body 20. A convex outer diameter portion 31 that becomes narrower and a convex inner diameter portion 32 that is uniform in width from the convex outer diameter portion 31 and that is closer to the inner diameter side than the small flange portion 2b of the inner ring 2 and to the vicinity of the inner ring raceway surface 2a are formed. Has been. A convex portion 30 is constituted by the convex outer diameter portion 31 and the convex inner diameter portion 32.
The cage 5 is positioned in the circumferential direction by the side surface 31b of the convex outer diameter portion 31 being a roller guide surface and abutting the tapered roller 4, and is guided by the tapered roller 4 during rotation.

柱部８の内周面８ａ、すなわち凸部内径部３２の内周面３２ａとこの内周面３２ａから連なる凸部外径部３１と柱部本体２０の内周面３１ａ、２０ａは、例えば図５に示すように、円弧状に形成された円弧部４０を備えている。   The inner peripheral surface 8a of the column portion 8, that is, the inner peripheral surface 32a of the convex portion inner diameter portion 32, the convex outer diameter portion 31 continuous from the inner peripheral surface 32a, and the inner peripheral surfaces 31a and 20a of the column main body 20 are, for example, As shown in FIG. 5, an arc portion 40 formed in an arc shape is provided.

円弧部４０は、内径側の回転軸Ｏに対する傾きが外径側の回転軸Ｏに対する傾きより大きく形成されている。すなわち、凸部内径部３２の内周面３２ａの回転軸Ｏに対する傾きが、柱部本体２０の内周面２０ａの回転軸Ｏに対する傾きより大きく形成されている。   The arc portion 40 is formed so that the inclination with respect to the rotation axis O on the inner diameter side is larger than the inclination with respect to the rotation axis O on the outer diameter side. That is, the inclination with respect to the rotation axis O of the inner peripheral surface 32 a of the convex inner diameter portion 32 is formed larger than the inclination with respect to the rotation axis O of the inner peripheral surface 20 a of the columnar body 20.

したがって、隣接する円すいころ４と柱部８の内周面８ａと内輪軌道面２ａとの径方向距離により定義される断面積は図１に示すように、小径環状部６側の断面積Ａ１より外径環状部７側の断面積Ａ２の方が大きくなっている。   Therefore, as shown in FIG. 1, the sectional area defined by the radial distance between the adjacent tapered roller 4, the inner peripheral surface 8a of the column portion 8, and the inner ring raceway surface 2a is larger than the sectional area A1 on the small-diameter annular portion 6 side. The cross-sectional area A2 on the outer diameter annular portion 7 side is larger.

保持器５の大径環状部７は、その内周面７ａが円すいころのピッチ円直径Ｐより外径側に位置するように形成され、内輪２の大鍔部２ｃと大径環状部７の内周面７ａとの間には潤滑油排出用の開口が確保されている。   The large-diameter annular portion 7 of the cage 5 is formed such that its inner peripheral surface 7 a is positioned on the outer diameter side from the pitch circle diameter P of the tapered roller, and the large collar portion 2 c of the inner ring 2 and the large-diameter annular portion 7 An opening for discharging the lubricating oil is secured between the inner peripheral surface 7a.

保持器５は、樹脂からなり、樹脂材料としては、ポリアミド４６やポリアミド６６などのポリアミド系樹脂、ポリブチレンテレフタレート、ポリフェレンサルサイド（ＰＰＳ）、ポリアミドイミド（ＰＡＩ）、熱可塑性ポリイミド、ポリエーテルエーテルケトン（ＰＥＥＫ）、ポリエーテルニトリル（ＰＥＮ）などが例示される。また、上記樹脂に、例えば、ガラス繊維や炭素繊維などの繊維状充填材を１０〜５０ｗｔ％程度適宜添加することによって、保持器５の剛性および寸法精度を向上させることができる。なお、保持器は金属により形成してもよいが、合成樹脂により形成することで保持器自体の慣性質量を十分に小さくでき、その分だけ、軸受の軽量化や回転速度の高速化を図ることができる。   The cage 5 is made of resin, and the resin materials include polyamide resins such as polyamide 46 and polyamide 66, polybutylene terephthalate, polyferlen salside (PPS), polyamide imide (PAI), thermoplastic polyimide, polyether ether ketone. (PEEK), polyether nitrile (PEN) and the like are exemplified. Moreover, the rigidity and dimensional accuracy of the cage 5 can be improved by appropriately adding about 10 to 50 wt% of a fibrous filler such as glass fiber or carbon fiber to the resin. The cage may be made of metal, but the inertial mass of the cage itself can be made sufficiently small by forming it with a synthetic resin, thereby reducing the weight of the bearing and increasing the rotational speed accordingly. Can do.

上記のように構成された円すいころ軸受１では、軸受の回転に伴うポンプ作用によって、潤滑油が内輪２の小鍔部２ｂと保持器５の小径環状部６の内周面６ａとの隙間からラビリンスシール部１１を介して軸受内部に流入し、円すいころ軸受１の回転による遠心力により大径環状部７側の開口から流出する。   In the tapered roller bearing 1 configured as described above, the lubricating oil flows from the gap between the small flange portion 2b of the inner ring 2 and the inner peripheral surface 6a of the small-diameter annular portion 6 of the retainer 5 by the pump action accompanying the rotation of the bearing. It flows into the inside of the bearing through the labyrinth seal portion 11 and flows out from the opening on the large-diameter annular portion 7 side by centrifugal force due to the rotation of the tapered roller bearing 1.

本実施形態の円すいころ軸受１によれば、柱部８の内周面８ａに、小径側における回転軸Ｏに対する傾きが大径側における回転軸Ｏに対する傾きより大きい円弧状の円弧部４０が形成されているので、内輪２の内輪軌道面２ａと保持器５の柱部８の内周面８ａにより形成される隙間面積が小径環状部側で小さく、大径環状部側で大きくなり、ポンプ効果の影響が強くなる。これにより、軸受内部の潤滑油の排出が促進され、攪拌トルクを低減することができる。   According to the tapered roller bearing 1 of the present embodiment, the arcuate arc portion 40 is formed on the inner peripheral surface 8a of the column portion 8 so that the inclination with respect to the rotation axis O on the small diameter side is larger than the inclination with respect to the rotation axis O on the large diameter side. Therefore, the gap area formed by the inner ring raceway surface 2a of the inner ring 2 and the inner peripheral surface 8a of the column part 8 of the cage 5 is small on the small diameter annular part side and large on the large diameter annular part side, and the pump effect The influence of becomes stronger. Thereby, discharge | emission of the lubricating oil inside a bearing is accelerated | stimulated, and stirring torque can be reduced.

更に、図５の矢印で示すように、柱部８の内周面８ａは、小径環状部６側から大径環状部７に向って次第に拡径するので、円すいころ軸受１内に滞留する潤滑油は、円すいころ軸受１の回転に伴って生じる遠心力によって内周面８ａに案内されて矢印方向の潤滑油の流れが生じ、円すいころ軸受１からの排出が促進される。   Furthermore, as indicated by the arrows in FIG. 5, the inner peripheral surface 8 a of the column portion 8 gradually increases in diameter from the small-diameter annular portion 6 toward the large-diameter annular portion 7, so that the lubricant staying in the tapered roller bearing 1 is retained. The oil is guided to the inner peripheral surface 8a by the centrifugal force generated with the rotation of the tapered roller bearing 1, and a flow of lubricating oil in the direction of the arrow is generated, and the discharge from the tapered roller bearing 1 is promoted.

さらに、保持器５の大径環状部７の内周面７ａは円すいころのピッチ円直径Ｐより外径側に位置するように形成されているので、内輪２の大鍔部２ｃと大径環状部７の内周面７ａとの間には大きな開口面積が確保されている。したがって、潤滑油が軸受空間から外部に流出するための隙間（開口）の面積を大きくとることができ、潤滑油の排出性が向上する。   Furthermore, since the inner peripheral surface 7a of the large-diameter annular portion 7 of the cage 5 is formed to be positioned on the outer diameter side from the pitch circle diameter P of the tapered roller, the large collar portion 2c of the inner ring 2 and the large-diameter annular A large opening area is secured between the inner peripheral surface 7a of the portion 7 and the inner peripheral surface 7a. Accordingly, the area of the gap (opening) for the lubricating oil to flow out of the bearing space can be increased, and the lubricating oil discharge performance is improved.

また、本実施形態における円すいころ軸受１においては、小径環状部６の内周面６ａと小鍔部２ｂの外周面とによってラビリンスシール部１１が形成されているので、このラビリンスシール部１１の隙間を調整することにより円すいころ軸受１内に流入する潤滑油量を調整でき、攪拌トルクを低減することができる。   Further, in the tapered roller bearing 1 according to this embodiment, the labyrinth seal portion 11 is formed by the inner peripheral surface 6a of the small-diameter annular portion 6 and the outer peripheral surface of the small flange portion 2b. By adjusting the amount, the amount of lubricating oil flowing into the tapered roller bearing 1 can be adjusted, and the stirring torque can be reduced.

さらに、保持器５の柱部８に設けられた凸部３０の体積分だけ円すいころ軸受１の内部空間の体積は狭くなる。これによって軸受１の内部空間の潤滑油量も少なくすることができ攪拌トルクを低減することができる。なお本実施形態において、図１に示すように凸部３０の最内径部３３は内輪２の小鍔部２ｂより内径側に位置しているが必ずしも小鍔部２ｂよりも内径側である必要はなく、ピッチ円直径Ｐ上又はピッチ円直径Ｐより内径側であればよい。   Furthermore, the volume of the internal space of the tapered roller bearing 1 is reduced by the volume of the convex portion 30 provided on the column portion 8 of the cage 5. As a result, the amount of lubricating oil in the internal space of the bearing 1 can be reduced, and the stirring torque can be reduced. In the present embodiment, as shown in FIG. 1, the innermost diameter portion 33 of the convex portion 30 is located on the inner diameter side of the small collar portion 2b of the inner ring 2, but it is not necessarily required to be on the inner diameter side of the small collar portion 2b. However, it may be on the pitch circle diameter P or on the inner diameter side from the pitch circle diameter P.

＜第２実施形態＞
第２実施形態の円すいころ軸受は、保持器の柱部形状が異なる以外は、本発明の第１実施形態の円すいころ軸受と同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 Second Embodiment
The tapered roller bearing according to the second embodiment is the same as the tapered roller bearing according to the first embodiment of the present invention except that the shape of the column of the cage is different. The description will be simplified or omitted.

第２実施形態の円すいころ軸受に使用される保持器５Ａは、図６に示すように、第１実施形態における保持器５において、柱部本体２０の内周面２０ａを円弧部４０から、内周面２０ａの傾きが外周面の傾きと略同一に形成された平行部５０とする。   As shown in FIG. 6, the cage 5A used in the tapered roller bearing of the second embodiment includes an inner circumferential surface 20a of the column body 20 from the arc portion 40 in the cage 5 of the first embodiment. Let the inclination of the peripheral surface 20a be the parallel part 50 formed substantially the same as the inclination of the outer peripheral surface.

これにより第２実施形態の保持器５Ａにおいても、第１実施形態と同様の効果を得ることができる。   Thereby, also in the holder | retainer 5A of 2nd Embodiment, the effect similar to 1st Embodiment can be acquired.

＜第３実施形態＞
第３実施形態の円すいころ軸受は、保持器の柱部形状が異なる以外は、本発明の第１実施形態の円すいころ軸受と同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 <Third Embodiment>
The tapered roller bearing according to the third embodiment is the same as the tapered roller bearing according to the first embodiment of the present invention except that the shape of the retainer column is different. The description will be simplified or omitted.

第３実施形態の円すいころ軸受に使用される保持器５Ｂは、図７に示すように、第１実施形態における保持器５において、柱部本体２０の内周面２０ａを円弧部４０から、テーパ部６０とする。   As shown in FIG. 7, the cage 5B used in the tapered roller bearing of the third embodiment is such that, in the cage 5 of the first embodiment, the inner peripheral surface 20a of the pillar body 20 is tapered from the arc portion 40. Part 60.

テーパ部６０は、その内周面も略直線状に形成され、その内周面の回転軸Ｏに対する傾きがその外周面の回転軸Ｏに対する傾きより大きく形成され、柱部本体２０の径方向長さ（厚さ）が小径環状部６側から外径環状部７側に向かって小さくなっている。   The taper portion 60 also has an inner peripheral surface formed in a substantially linear shape, and the inclination of the inner peripheral surface with respect to the rotation axis O is larger than the inclination of the outer peripheral surface with respect to the rotation axis O. The thickness (thickness) decreases from the small-diameter annular portion 6 side toward the outer-diameter annular portion 7 side.

これにより第３実施形態の保持器５Ｂにおいても、第１実施形態と同様の効果を得ることができる。   Thereby, also in the holder | retainer 5B of 3rd Embodiment, the effect similar to 1st Embodiment can be acquired.

＜第４実施形態＞
第４実施形態の円すいころ軸受は、保持器の柱部形状が異なる以外は、本発明の第１実施形態の円すいころ軸受と同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 <Fourth embodiment>
The tapered roller bearing according to the fourth embodiment is the same as the tapered roller bearing according to the first embodiment of the present invention except that the shape of the retainer column is different. The description will be simplified or omitted.

第４実施形態の円すいころ軸受に使用される保持器５Ｃは、図８に示すように、第１実施形態における保持器５において、凸部外径部３１の内周面３１ａを円弧部４０から内周面の傾きが外周面の傾きより大きく形成されたテーパ部６０とし、柱部本体２０の内周面２０ａをテーパ部６０から内周面２０ａの傾きが外周面の傾きと略同一に形成された平行部５０とする。   As shown in FIG. 8, the cage 5 </ b> C used in the tapered roller bearing of the fourth embodiment is such that the inner peripheral surface 31 a of the convex outer diameter portion 31 extends from the arc portion 40 in the cage 5 of the first embodiment. The inner peripheral surface 20a of the pillar body 20 is formed so that the inclination of the inner peripheral surface 20a from the tapered portion 60 is substantially the same as the inclination of the outer peripheral surface. It is assumed that the parallel part 50 is made.

これにより第４実施形態の保持器５Ｃにおいても、第１実施形態と同様の効果を得ることができる。なお、第４実施形態の保持器５Ｃにおいて、柱部本体２０の内周面２０ａを円弧部４０又はテーパ部６０としても同様の効果を得ることができる。
＜第５実施形態＞
第５実施形態の円すいころ軸受は、保持器の柱部形状が異なる以外は、本発明の第１実施形態の円すいころ軸受と同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 Thereby, also in the holder | retainer 5C of 4th Embodiment, the effect similar to 1st Embodiment can be acquired. In the cage 5C of the fourth embodiment, the same effect can be obtained even when the inner peripheral surface 20a of the columnar body 20 is the arc portion 40 or the tapered portion 60.
<Fifth Embodiment>
The tapered roller bearing according to the fifth embodiment is the same as the tapered roller bearing according to the first embodiment of the present invention except that the shape of the column of the cage is different. The description will be simplified or omitted.

第５実施形態の円すいころ軸受に使用される保持器５Ｄは、図９に示すように、第１実施形態における保持器５において、凸部内径部３２の内周面３２ａを円弧部４０から内周面の傾きが外周面の傾きより大きく形成されたテーパ部６０とし、柱部本体２０の内周面２０ａを円弧部４０から内周面２０ａの傾きが外周面の傾きと略同一に形成された平行部５０とする。   As shown in FIG. 9, the cage 5D used in the tapered roller bearing of the fifth embodiment is configured so that the inner peripheral surface 32a of the convex inner diameter portion 32 extends from the arc portion 40 in the cage 5 of the first embodiment. The tapered portion 60 is formed so that the inclination of the peripheral surface is larger than the inclination of the outer peripheral surface, and the inner peripheral surface 20a of the column body 20 is formed so that the inclination of the inner peripheral surface 20a from the arc portion 40 is substantially the same as the inclination of the outer peripheral surface. The parallel part 50 is used.

これにより第５実施形態の保持器５Ｄにおいても、第１実施形態と同様の効果を得ることができる。なお、第５実施形態の保持器５Ｄにおいて、柱部本体２０の内周面２０ａを円弧部４０又はテーパ部６０としても同様の効果を得ることができる。   Thereby, also in the holder | retainer 5D of 5th Embodiment, the effect similar to 1st Embodiment can be acquired. In the cage 5D of the fifth embodiment, the same effect can be obtained even when the inner peripheral surface 20a of the column part body 20 is the arc part 40 or the taper part 60.

＜第６実施形態＞
第６実施形態の円すいころ軸受は、保持器の柱部形状が異なる以外は、本発明の第１実施形態の円すいころ軸受と同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 <Sixth Embodiment>
The tapered roller bearing according to the sixth embodiment is the same as the tapered roller bearing according to the first embodiment of the present invention except that the shape of the retainer column is different. The description will be simplified or omitted.

第６実施形態の円すいころ軸受に使用される保持器５Ｅは、図１０に示すように、第１実施形態における保持器５において、柱部８の円周方向両側面８ｂ、すなわち柱部８を構成する柱部本体２０、凸部外径部３１及び凸部内径部３２の円周方向両側面２０ｂ、３１ｂ、３２ｂを円すいころ４の形状に沿った円弧形状とする。なお、柱部内周面の形状は第１実施形態と同一である。   As shown in FIG. 10, the cage 5E used in the tapered roller bearing of the sixth embodiment is similar to the cage 5 of the first embodiment. The circumferential side surfaces 20b, 31b, and 32b of the column main body 20, the convex outer diameter portion 31, and the convex inner diameter portion 32 are formed into an arc shape along the shape of the tapered roller 4. The shape of the inner peripheral surface of the column part is the same as that in the first embodiment.

ここで円すいころ４のピッチ円直径Ｐの位置における柱部８の周方向側面８ｂと円すいころ４の周方向の隙間（ポケット隙間）は０．０５〜０．４ｍｍであることが望ましい。ポケット隙間が０．０５ｍｍ以下では円すいころ４が柱部８により拘束される可能性があり、０．４ｍｍ以上では回転中に保持器５の振れ回りが大きくなって振動が増大し、トルクが増大する原因となる可能性がある。   Here, the circumferential gap (pocket gap) between the circumferential side surface 8b of the column 8 and the tapered roller 4 at the position of the pitch circle diameter P of the tapered roller 4 is preferably 0.05 to 0.4 mm. If the pocket clearance is 0.05 mm or less, the tapered roller 4 may be restrained by the column portion 8. If the pocket clearance is 0.4 mm or more, the whirling of the cage 5 becomes large during rotation, increasing vibration and increasing torque. May cause

本実施形態の円すいころ軸受１によれば、第１実施形態の円すいころ軸受の効果に加え、円すいころ軸受１の内部空間の体積がさらに減少し、軸受内部の潤滑油の潤滑油量を減らすことができ、攪拌トルクをさらに低減させることができる。また、ポケット９を構成する柱部８の円周方向両側面８ｂを円すいころ４の形状に沿った円弧形状とすることで、保持器５と円すいころ４の接触可能な面積が増えるため、円すいころ４にスキューが発生して傾くとすぐに柱部８の側面８ｂと接触してスキューが矯正され、円すいころのスキューを抑制することができる。したがって、スキューに起因して発生するトルクの変動をも抑制することができる。   According to the tapered roller bearing 1 of the present embodiment, in addition to the effect of the tapered roller bearing of the first embodiment, the volume of the internal space of the tapered roller bearing 1 is further reduced, and the amount of lubricating oil in the lubricating oil inside the bearing is reduced. The stirring torque can be further reduced. Moreover, since the area where the cage 5 and the tapered roller 4 can be brought into contact with each other is increased by making the circumferential side both sides 8b of the column portion 8 constituting the pocket 9 into an arc shape along the shape of the tapered roller 4, the tapered shape. As soon as the roller 4 is skewed and tilted, it comes into contact with the side surface 8b of the column portion 8 to correct the skew, and the skew of the tapered roller can be suppressed. Therefore, it is possible to suppress torque fluctuations caused by skew.

なお、本実施形態は、第１実施形態に限らず、第２〜第６実施形態の円すいころ軸受にも適用することができる。   In addition, this embodiment can be applied not only to the first embodiment but also to the tapered roller bearings of the second to sixth embodiments.

＜第７実施形態＞
第７実施形態の円すいころ軸受は、保持器の柱部形状が異なる以外は、本発明の第６実施形態の円すいころ軸受と同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 <Seventh embodiment>
The tapered roller bearing according to the seventh embodiment is the same as the tapered roller bearing according to the sixth embodiment of the present invention except that the shape of the column of the cage is different. The description will be simplified or omitted.

第７実施形態の円すいころ軸受に使用される保持器５Ｆは、図１１に示すように、第６実施形態における保持器５Ｅにおいて、柱部８の円周方向両側面８ｂのうち柱部８を構成する柱部本体２０及び凸部外径部３１の円周方向両側面２０ｂ、３１ｂを円すいころ４の形状に沿った円弧形状とし、凸部内径部３２の円周方向両側面３２ｂを一様の幅を有するように構成する。   As shown in FIG. 11, the cage 5F used for the tapered roller bearing of the seventh embodiment is the cage 5E of the sixth embodiment. The circumferential side surfaces 20b, 31b of the column main body 20 and the convex outer diameter portion 31 constituting the circular arc shape along the shape of the tapered roller 4 are formed, and the circumferential side surfaces 32b of the convex inner diameter portion 32 are uniform. The width is configured as follows.

これにより、第６実施形態の円すいころ軸受１と同様の効果を得ることができる。さらに、第６実施形態の円すいころ軸受１と比較して、円すいころ４の組込み性が向上する。   Thereby, the effect similar to the tapered roller bearing 1 of 6th Embodiment can be acquired. Furthermore, as compared with the tapered roller bearing 1 of the sixth embodiment, the assemblability of the tapered roller 4 is improved.

尚、本発明は、前述した各実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。例えば、本実施形態において保持器として大径環状部７を備えた保持器を例示したが、大径環状部を備えていない、いわゆるくし型保持器であってもよい。   In addition, this invention is not limited to each embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. For example, although the cage provided with the large-diameter annular portion 7 is illustrated as the cage in the present embodiment, a so-called comb-type cage that does not include the large-diameter annular portion may be used.

１ 円すいころ軸受
２ 内輪
２ａ 内輪軌道面
２ｂ 小鍔部
３ 外輪
３ａ 外輪軌道面
４ 円すいころ
５、５Ａ、５Ｂ、５Ｃ、５Ｄ、５Ｅ、５Ｆ 保持器
６ 小径環状部
７ 大径環状部
８ 柱部
８ａ 柱部内周面
８ｂ 柱部の周方向側面
９ ポケット
１１ ラビリンスシール部
２０ 柱部本体
２０ａ 柱部本体の内周面
２０ａ 柱部本体の周方向側面
３０ 凸部
３１ 外径側凸部
３１ａ 外径側凸部の内周面
３１ｂ 外径側凸部の周方向側面
３２ 内径側凸部
３２ａ 内径側凸部の内周面
３２ａ 外径側凸部の周方向側面
４０ 円弧部
５０ 平行部
６０ テーパ部
Ｏ 回転軸
Ｐ ピッチ円すい面 DESCRIPTION OF SYMBOLS 1 Tapered roller bearing 2 Inner ring 2a Inner ring raceway surface 2b Small collar part 3 Outer ring 3a Outer ring raceway surface 4 Tapered rollers 5, 5A, 5B, 5C, 5D, 5E, 5F Cage 6 Small diameter annular part 7 Large diameter annular part 8 Column part 8a Column part inner peripheral surface 8b Column part circumferential side surface 9 Pocket 11 Labyrinth seal part 20 Column part main body 20a Column part body inner peripheral surface 20a Column part body circumferential side surface 30 Convex part 31 Outer diameter side convex part 31a Outer diameter Inner circumferential surface 31b of the side convex portion Circumferential side surface 32 of the outer diameter side convex portion Inner diameter side convex portion 32a Inner circumferential surface 32a of the inner diameter side convex portion Circumferential side surface 40 of the outer diameter side convex portion Arc portion 50 Parallel portion 60 Tapered portion O Rotating shaft P Pitch conical surface

Claims (4)

内輪と、外輪と、前記内輪と前記外輪の間を周方向に転動可能な複数の円すいころと、前記複数の円すいころを所定の間隔で保持する樹脂製保持器とを備え、油潤滑で使用される円すいころ軸受であって、
保持器柱部は、小径側における柱部内周面の回転軸に対する傾きが、大径側における柱部内周面の回転軸に対する傾きより大きく、軸受内部の潤滑油の排出を促進する円弧部を備え、
前記保持器柱部は前記保持器の小径環状部と大径環状部を連接し、
前記保持器の前記小径環状部は、内周面が前記内輪の小鍔部の外周面に対向してラビリンスシールを構成し、
前記柱部の最内径部は前記小鍔部の外周面よりも内径側に位置し、
前記大径環状部の内周面は、前記円すいころのピッチ円直径より外径側に位置することを特徴とする円すいころ軸受。 An inner ring, an outer ring, a plurality of tapered rollers capable of rolling in a circumferential direction between the inner ring and the outer ring, and a resin cage that holds the plurality of tapered rollers at a predetermined interval. A tapered roller bearing used,
The cage column portion has an arc portion that has an inclination with respect to the rotation axis of the inner circumferential surface of the column portion on the small diameter side that is larger than an inclination with respect to the rotation axis of the inner circumferential surface of the column portion on the large diameter side, and promotes discharge of lubricating oil inside the bearing. ,
The retainer column portion connects the small diameter annular portion and the large diameter annular portion of the retainer,
The small-diameter annular portion of the cage constitutes a labyrinth seal with an inner peripheral surface facing an outer peripheral surface of the small collar portion of the inner ring,
The innermost diameter part of the column part is located on the inner diameter side of the outer peripheral surface of the small collar part,
A tapered roller bearing , wherein an inner peripheral surface of the large-diameter annular portion is located on an outer diameter side with respect to a pitch circle diameter of the tapered roller. 前記円弧部は、前記柱部の前記最内径部に連なっていることを特徴とする請求項１に記載の円すいころ軸受。  The tapered roller bearing according to claim 1, wherein the arc portion is continuous with the innermost diameter portion of the column portion. 前記円弧部の外径側端部は、前記円すいころのピッチ円直径より外径側に位置することを特徴とする請求項１又は２に記載の円すいころ軸受。 The tapered roller bearing according to claim 1 or 2 , wherein an end portion on the outer diameter side of the arc portion is positioned on an outer diameter side with respect to a pitch circle diameter of the tapered roller. 前記柱部内周面が略直線状に形成され前記柱部内周面の傾きが柱部外周面の傾きと同一に形成された平行部を備え、
前記平行部は、前記円弧部の外径側端部から連続して形成されることを特徴とする請求項１〜３のいずれか１項に記載の円すいころ軸受。 The columnar inner peripheral surface is formed in a substantially linear shape, and the columnar inner peripheral surface has a parallel portion formed with the same inclination as the columnar outer peripheral surface,
The tapered roller bearing according to any one of claims 1 to 3, wherein the parallel portion is formed continuously from an outer diameter side end portion of the arc portion.
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160040716A1 (en) * 2013-04-04 2016-02-11 Nsk Ltd. Resin cage for tapered roller bearing and tapered roller bearing including the resin cage
US10302131B2 (en) 2012-12-25 2019-05-28 Nsk Ltd. Tapered roller bearing
CN111894973A (en) * 2020-08-10 2020-11-06 洛阳Lyc轴承有限公司 Double-row tapered roller bearing with copper retainer structure

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020102087A1 (en) * 2020-01-29 2021-07-29 Schaeffler Technologies AG & Co. KG Roller bearings with a bearing cage optimized for lubrication passage

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Publication number Priority date Publication date Assignee Title
DE3728877A1 (en) * 1987-08-29 1989-03-09 Kugelfischer G Schaefer & Co Tapered roller bearings
NL1010499C2 (en) * 1998-11-06 2000-05-09 Skf Eng & Res Centre Bv Grease lubricated tapered roller bearing.
JP2002227849A (en) * 2001-01-29 2002-08-14 Nsk Ltd Tapered roller bearing retainer and double row tapered roller bearing unit

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10302131B2 (en) 2012-12-25 2019-05-28 Nsk Ltd. Tapered roller bearing
US20160040716A1 (en) * 2013-04-04 2016-02-11 Nsk Ltd. Resin cage for tapered roller bearing and tapered roller bearing including the resin cage
US9995341B2 (en) 2013-04-04 2018-06-12 Nsk Ltd. Resin cage for tapered roller bearing and tapered roller bearing including the resin cage
CN111894973A (en) * 2020-08-10 2020-11-06 洛阳Lyc轴承有限公司 Double-row tapered roller bearing with copper retainer structure

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