JP2007078147A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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JP2007078147A
JP2007078147A JP2005270349A JP2005270349A JP2007078147A JP 2007078147 A JP2007078147 A JP 2007078147A JP 2005270349 A JP2005270349 A JP 2005270349A JP 2005270349 A JP2005270349 A JP 2005270349A JP 2007078147 A JP2007078147 A JP 2007078147A
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tapered roller
cage
pocket
roller bearing
lubricating oil
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JP4823624B2 (en
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Takashi Tsujimoto
崇 辻本
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2005270349A priority Critical patent/JP4823624B2/en
Priority to PCT/JP2006/318353 priority patent/WO2007032470A1/en
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Abstract

<P>PROBLEM TO BE SOLVED: To improve assembly efficiency of a tapered roller bearing; and to reduce rotational torque. <P>SOLUTION: A rib end 5d of a retainer 5 is bent to an axial direction inner side, and thereby, a tapered roller is supported by a small annular part 5a of the retainer and the rib end when a small diameter end face of the tapered roller is caught by a pocket 6 when assembling the tapered roller to the retainer. Accordingly, the tapered roller is held in the stable posture, and the tapered roller is smoothly assembled without being tilted to the circumferential direction. Further, circulation of lubricating oil is improved by a cutout in a pillar part of the pocket of the retainer on a narrow side, and an amount of the lubricating oil retained in the bearing is reduced, and torque by flow resistance of the lubricating oil is reduced. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は円錐ころ軸受に関し、特に自動車のトランスミッションの歯車装置に好適に組み込まれる円錐ころ軸受に関する。   The present invention relates to a tapered roller bearing, and more particularly to a tapered roller bearing that is suitably incorporated in a gear device of an automobile transmission.

自動車のトランスミッション（主変速機）は大別するとマニュアルタイプとオートマチックタイプがあり、また車輌の駆動方式によって前輪駆動（ＦＷＤ）用トランスアクスル、後輪駆動（ＲＷＤ）用トランスミッション、および四輪駆動（４ＷＤ）用トランスファ（副変速機）がある。これらは、エンジンからの駆動力を変速して駆動軸などへ伝達するものである。   Automobile transmissions (main transmissions) are broadly classified into manual types and automatic types. Depending on the vehicle drive system, front wheel drive (FWD) transaxle, rear wheel drive (RWD) transmission, and four wheel drive (4WD) ) Transfer (sub-transmission). These shift the driving force from the engine and transmit it to the drive shaft or the like.

上記のような自動車のトランスミッションは、近年、ミッションのＡＴ化、ＣＶＴ化および低燃費化等のために低粘度の油が使われる傾向にある。低粘度オイルが使用される環境化では、（１）油温が高い、（２）油量が少ない、（３）予圧抜けが発生するなどの悪条件が重なった場合に、潤滑不良に起因する非常に短寿命の表面起点剥離が面圧の高い内輪軌道面に生じることがある。   In recent years, low-viscosity oils tend to be used for transmissions of automobiles as described above for AT, CVT, and fuel efficiency reduction of missions. In an environment where low-viscosity oil is used, it is caused by poor lubrication when adverse conditions such as (1) high oil temperature, (2) low oil volume, and (3) preload loss occur. Very short-life surface-origin separation may occur on the inner ring raceway surface with high surface pressure.

この表面起点剥離による短寿命対策としては最大面圧低減が直接的かつ有効な解決策である。最大面圧を低減するためには、例えば、軸受の円錐ころの本数を増大させる方法がある。円錐ころの直径を減少させないで本数を増やすためには、保持器のポケット間隔（柱部）を狭くしなければならないが、保持器の柱部は円錐ころを摺接支持するための強度を確保するため、一定以上の幅が必要である。よって、保持器の柱部の幅を維持しながら円錐ころの本数を増やすために、保持器のピッチ円を大きくして外輪側にできるだけ寄せる必要がある。   As a countermeasure for short life due to this surface-origin separation, reduction of the maximum surface pressure is a direct and effective solution. In order to reduce the maximum surface pressure, for example, there is a method of increasing the number of tapered rollers of the bearing. In order to increase the number of tapered rollers without reducing the diameter of the tapered rollers, the pocket spacing (columns) of the cage must be narrowed, but the columns of the cage ensure strength to support the sliding contact with the tapered rollers. Therefore, a certain width or more is necessary. Therefore, in order to increase the number of tapered rollers while maintaining the width of the pillar portion of the cage, it is necessary to increase the pitch circle of the cage as close as possible to the outer ring side.

その方法として、例えば特許文献１に示されている円錐ころ軸受では、保持器の外径面に突起部が設けられている。これにより、円錐ころ軸受の回転時には、突起部と外輪内径面との間に形成される楔状油膜の動圧により保持器と外輪との間の微小隙間が維持され、両者の接触に伴うトルク損失や保持器ないし外輪軌道面の損傷が防止される。従って保持器外径面を可及的に外輪内径面に接することなく近接させることが可能となり、保持器のピッチ円を拡径できる。
特開２００５−９８３１６号公報 As a method, for example, in the tapered roller bearing shown in Patent Document 1, a protrusion is provided on the outer diameter surface of the cage. As a result, during the rotation of the tapered roller bearing, a minute gap between the cage and the outer ring is maintained by the dynamic pressure of the wedge-shaped oil film formed between the protrusion and the inner surface of the outer ring, and torque loss due to contact between the two is maintained. And damage to the cage or the outer ring raceway surface is prevented. Accordingly, the outer diameter surface of the cage can be made as close as possible without contacting the inner diameter surface of the outer ring, and the pitch circle of the cage can be enlarged.
JP 2005-98316 A

しかしながら、上記のように保持器のピッチ円を拡径することにより、円錐ころを保持器への組付ける際に以下のような不具合を生じる。円錐ころの保持器への組付けは、保持器を小環状部が下方になるように設置し、円錐ころを上方から小径端面を下にして保持器のポケット（小環状部）に引っ掛かるまで降下させ、円錐ころを径方向外側に傾斜させることにより行われる。円錐ころの小径端面がポケットに引っ掛かったときは、円錐ころが保持器の小環状部のみによって支持されているため、非常に不安定である。保持器のピッチ面を拡径すると、円錐ころがポケットに引っ掛かる部分が小さくなることでさらに不安定になり、円錐ころが円周方向に傾倒してしまい、組立が困難となる。   However, by enlarging the pitch circle of the cage as described above, the following problems occur when the tapered roller is assembled to the cage. Assemble the tapered roller to the cage by placing the cage so that the small annular part is at the bottom, and lowering the tapered roller from above with the small diameter end face down until it is caught in the pocket (small annular part) of the cage And the tapered roller is tilted radially outward. When the small-diameter end surface of the tapered roller is caught in the pocket, the tapered roller is supported only by the small annular portion of the cage, so that it is very unstable. When the pitch surface of the cage is increased in diameter, the portion where the tapered roller is caught in the pocket becomes smaller, which makes the tapered roller more unstable and tilts in the circumferential direction, making assembly difficult.

また、円錐ころの本数を増やすことにより、軸受内部の潤滑油による流動抵抗が増し、回転トルクは増大する。   Further, by increasing the number of tapered rollers, the flow resistance due to the lubricating oil inside the bearing is increased, and the rotational torque is increased.

本発明は、円錐ころ軸受の組付け性を向上し、且つ回転トルクを低減することを目的とする。   An object of this invention is to improve the assembly | attachment property of a tapered roller bearing, and to reduce rotational torque.

上記の課題を解決するために、本発明は、内輪と、外輪と、前記内輪と外輪との間に転動自在に配された複数の円錐ころと、前記円錐ころを円周所定間隔に収納するポケットを有する保持器とを備え、前記保持器が、前記円錐ころの小径側で連なる小環状部と、円錐ころの大径側で連なる大環状部と、これらの環状部を連結する複数の柱部とからなり、前記ポケットが、前記円錐ころの小径側を収納する部分が狭幅側、大径側を収納する部分が広幅側となる台形状に形成された円錐ころ軸受において、前記保持器の小環状部の端縁から径方向にリブを延在させ、そのリブの先端部を軸方向内側に屈曲させた形状とし、且つ、前記保持器の台形状ポケットの狭幅側の柱部に切り欠きを設けたことを特徴とする。   In order to solve the above-described problems, the present invention includes an inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and the tapered rollers stored at predetermined circumferential intervals. A retainer having a pocket to be connected, and the retainer includes a small annular portion that is continuous on the small diameter side of the tapered roller, a large annular portion that is continuous on the large diameter side of the tapered roller, and a plurality of portions that connect these annular portions. In the tapered roller bearing formed of a pillar portion, the pocket is formed in a trapezoidal shape in which a portion storing the small diameter side of the tapered roller is a narrow side and a portion storing the large diameter side is a wide side. A rib extending in the radial direction from the edge of the small annular portion of the vessel, the tip of the rib being bent inward in the axial direction, and the column portion on the narrow side of the trapezoidal pocket of the cage It is characterized by providing a notch.

上記のように、本発明では、保持器のリブ先端部を軸方向内側に屈曲させた形状とする。これにより、円錐ころを保持器に組付ける際、円錐ころの小径端面がポケットに引っ掛かったときに、円錐ころが保持器の小環状部とリブの先端部とで支持される。これにより、円錐ころが安定した姿勢に保持されるため、円錐ころが円周方向に傾倒することなくスムーズに組付けられる。   As described above, in the present invention, the rib tip of the cage is bent inward in the axial direction. Thus, when the tapered roller is assembled to the cage, the tapered roller is supported by the small annular portion of the cage and the tip of the rib when the small diameter end surface of the tapered roller is caught in the pocket. Thereby, since the tapered roller is held in a stable posture, the tapered roller is smoothly assembled without being inclined in the circumferential direction.

また、保持器の台形状ポケットの狭幅側の柱部に切り欠きを設けることにより、潤滑油の循環が良好になり、軸受内部に滞留する潤滑油の量を減らすことができる。よって、潤滑油の流動抵抗によるトルクが低減される。   Further, by providing a notch in the narrow-side column portion of the trapezoidal pocket of the cage, the circulation of the lubricating oil is improved and the amount of the lubricating oil staying inside the bearing can be reduced. Therefore, torque due to the flow resistance of the lubricating oil is reduced.

台形状ポケットの狭幅側の小環状部にも切欠きを設けると、軸受内の潤滑油の循環がさらに良好になり、トルク低減効果を増すことができる。   If a notch is provided also in the small annular portion on the narrow side of the trapezoidal pocket, the circulation of the lubricating oil in the bearing is further improved, and the torque reduction effect can be increased.

台形状ポケットの広幅側の少なくとも柱部に切り欠きを設けると、円錐ころをバランスよく柱部に摺接させることができる。   If a notch is provided in at least the column portion on the wide side of the trapezoidal pocket, the tapered roller can be slidably contacted with the column portion in a balanced manner.

台形状ポケットの狭幅側に設けた切り欠きの合計面積を、広幅側に設けた切り欠きの合計面積よりも広く設定することによっても、軸受内部に滞留する潤滑油の量を減らすことができる。   By setting the total area of the notches provided on the narrow side of the trapezoidal pocket wider than the total area of the notches provided on the wide side, the amount of lubricating oil staying inside the bearing can be reduced. .

以上のように、本発明によると、円錐ころ軸受の組付け性が向上し、且つ、回転トルクを低減することができる。   As described above, according to the present invention, the ease of assembly of the tapered roller bearing can be improved and the rotational torque can be reduced.

以下に本発明の一実施形態を図に基づいて説明する。   Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

図１に示す実施形態における円錐ころ軸受１は、円錐状の軌道面２ａを有する外輪２と、円錐状の軌道面３ａを有し、この軌道面３ａの小径側端部に小鍔部３ｂ、大径側端部に大鍔部３ｃを有する内輪３と、外輪２の軌道面２ａと内輪３の軌道面３ａとの間に転動自在に配された複数の円錐ころ４と、円錐ころ４を円周方向等間隔に保持する保持器５とを備えている。この円錐ころ軸受１は、内輪３に軸（図示せず）が同軸的に挿着され、外輪２がハウジング（図示せず）の内径に取り付けられることにより、例えば自動車のトランスミッションの軸支持部に組み付けられる。   A tapered roller bearing 1 in the embodiment shown in FIG. 1 has an outer ring 2 having a conical raceway surface 2a and a conical raceway surface 3a, and a small flange portion 3b at the small diameter side end of the raceway surface 3a. An inner ring 3 having a large flange 3c at the end on the large diameter side, a plurality of tapered rollers 4 disposed between the raceway surface 2a of the outer ring 2 and the raceway surface 3a of the inner ring 3, and a tapered roller 4 Is held at equal intervals in the circumferential direction. The tapered roller bearing 1 has a shaft (not shown) coaxially inserted into an inner ring 3 and an outer ring 2 attached to the inner diameter of a housing (not shown), so that, for example, a shaft support portion of a transmission of an automobile is used. Assembled.

保持器５は、例えばＳＰＣＣ鋼板等の鋼板（鋼管）からプレス加工によって成形されたプレス加工品で、図２に示すように、小環状部５ａと、大環状部５ｂと、小環状部５ａと大環状部５ｂとを軸方向に連結する複数の柱部５ｃと、円周方向に隣接する柱部５ｃ間に設けられ、円錐ころ４を転動自在に収容する複数のポケット６とを備えている。ポケット６は、円錐ころの小径側を収納する部分が狭幅側、大径側を収納する部分が広幅側となる台形状に形成され、狭幅側の柱部及び小環状部と、広幅側の柱部には、それぞれ切り欠き６ａ、６ｃ、６ｂが設けられる。小環状部５ａには、その端部から延在されたリブが備えられ、そのリブ先端部５ｄを軸方向内側に屈曲させた形状を有する。   The cage 5 is a pressed product formed by pressing from a steel plate (steel pipe) such as a SPCC steel plate, for example, and as shown in FIG. 2, a small annular portion 5a, a large annular portion 5b, and a small annular portion 5a A plurality of column portions 5c for connecting the macro-annular portion 5b in the axial direction, and a plurality of pockets 6 provided between the column portions 5c adjacent in the circumferential direction so as to accommodate the tapered rollers 4 in a rollable manner. Yes. The pocket 6 is formed in a trapezoidal shape in which a portion for storing the small diameter side of the tapered roller is a narrow side, and a portion for storing the large diameter side is a wide side, and a column portion and a small annular portion on the narrow side, and a wide side Notches 6a, 6c, and 6b are provided in the column portions, respectively. The small annular portion 5a is provided with a rib extending from an end portion thereof, and has a shape in which the rib tip portion 5d is bent inward in the axial direction.

柱部５ｃの外径面には図３、図４に示すように外輪軌道面側に向けて凸状を成す突起部５ｅが一体に形成されている。この突起部５ｅは、柱部５ｃの横断方向の断面輪郭形状が円弧状を成しており、この円弧状の曲率半径Ｒ２は外輪軌道面２ａの半径Ｒ１より小さく形成されている。これは突起部５ｅと外輪軌道面２ａとの間に良好な楔状油膜が形成されるようにするためであり、望ましくは突起部５ｅの曲率半径Ｒ２は外輪軌道面２ａの半径Ｒ１の７０〜９０％程度に形成するとよい。７０％未満であると楔状油膜の入口開き角度が大きくなり過ぎて却って動圧が低下する。また９０％を超えると楔状油膜の入口角度が小さくなり過ぎて同様に動圧が低下する。また、突起部５ｅの横幅Ｗ２は望ましくは柱部５ｃの横幅Ｗ１の５０％以上となるように形成する（Ｗ２≧０．５×Ｗ１）。５０％未満では良好な楔状油膜を形成するための充分な突起部５ｅの高さが確保できなくなるためである。なお、外輪軌道面２ａの半径Ｒ１は大径側から小径側へと連続的に変化しているので、突起部５ｅの曲率半径Ｒ２もそれに合わせて大径側環状部５ｂの大きな曲率半径Ｒ２から小径側環状部５ａの小さな曲率半径Ｒ２へと連続的に変化するようにする。   As shown in FIGS. 3 and 4, a protruding portion 5 e that protrudes toward the outer ring raceway surface is integrally formed on the outer diameter surface of the column portion 5 c. The projecting portion 5e has a circular cross-sectional contour shape of the column portion 5c, and the arc-shaped radius of curvature R2 is smaller than the radius R1 of the outer ring raceway surface 2a. This is so that a good wedge-shaped oil film is formed between the protrusion 5e and the outer ring raceway surface 2a. Preferably, the curvature radius R2 of the protrusion 5e is 70 to 90 of the radius R1 of the outer ring raceway surface 2a. It is good to form in about%. If it is less than 70%, the opening angle of the wedge-shaped oil film becomes too large, and the dynamic pressure decreases. If it exceeds 90%, the inlet angle of the wedge-shaped oil film becomes too small, and the dynamic pressure similarly decreases. Further, the lateral width W2 of the protruding portion 5e is desirably formed to be 50% or more of the lateral width W1 of the column portion 5c (W2 ≧ 0.5 × W1). This is because if it is less than 50%, a sufficient height of the projection 5e for forming a good wedge-shaped oil film cannot be secured. Since the radius R1 of the outer ring raceway surface 2a continuously changes from the large diameter side to the small diameter side, the radius of curvature R2 of the projection 5e is accordingly increased from the large radius of curvature R2 of the large diameter side annular portion 5b. The small radius side annular portion 5a is continuously changed to a small radius of curvature R2.

保持器５のポケット６に、図２に示すような切り欠きを設ける理由は以下のとおりである。円錐ころ軸受１は、下部が潤滑油の油浴に漬かった状態で使用されることが多い。円錐ころ１が、下部が油浴に漬かった状態で高速回転すると、図５に矢印で示すように、油浴の潤滑油が円錐ころ４の小径端面４ａ側から保持器５の外径側と内径側とに分かれて軸受内部へ流入する。保持器５の外径側から外輪２側へ流入する潤滑油は、外輪２の軌道面２ａには障害物がないため、その軌道面２ａに沿って円錐ころ４の大径端面４ｂ側へスムーズに通過して軸受内部から流出する。しかし、保持器５の内径側から内輪３側へ流入する潤滑油は、内輪３の大鍔部３ｃによりせき止められ、軸受内部に滞留しやすくなる。この滞留する潤滑油が、軸受回転に対する流動抵抗となって回転トルクを増大させる。   The reason why notches as shown in FIG. 2 are provided in the pocket 6 of the cage 5 is as follows. The tapered roller bearing 1 is often used with its lower part immersed in a lubricating oil bath. When the tapered roller 1 rotates at a high speed with the lower part immersed in an oil bath, the lubricating oil in the oil bath moves from the small-diameter end face 4a side of the tapered roller 4 to the outer diameter side of the cage 5 as shown by arrows in FIG. It is divided into the inner diameter side and flows into the bearing. The lubricating oil flowing from the outer diameter side of the retainer 5 to the outer ring 2 side is smoothly obstructed on the raceway surface 2a of the outer ring 2 and therefore smoothly moves toward the large diameter end surface 4b side of the tapered roller 4 along the raceway surface 2a. To flow out of the bearing. However, the lubricating oil flowing from the inner diameter side of the cage 5 to the inner ring 3 side is dammed by the large flange portion 3c of the inner ring 3 and tends to stay inside the bearing. This staying lubricating oil becomes a flow resistance against bearing rotation and increases the rotational torque.

保持器５の内径側から内輪３側へ流入する潤滑油は、保持器５のリブ先端部５ｄと内輪３の小鍔部３ｂとの隙間δを狭く設定することにより、保持器５の外径側から流入する潤滑油よりもはるかに少なくなり、さらに、この隙間δから流入する潤滑油の大半は、ポケット６の狭幅側の柱部５ｃに設けられた切り欠き６ａを通過して、保持器５の外径側へ移動する。したがって、そのまま内輪３の軌道面３ａに沿って大鍔部３ｃまでいたる潤滑油の量は非常に少なくなり、軸受内部に滞留する潤滑油の量を減らすことができるため、回転トルクを低減できる。本実施形態では、ポケット６の狭幅側の小環状部５ａにも切り欠き６ｃが設けられているため、内輪３側に流入した潤滑油をさらに外輪２側へ移動させることができ、回転トルクのさらなる低減が期待できる。また、ポケット６の狭幅側に設けた切り欠き６ａ、６ｃの合計面積を、広幅側に設けた切り欠き６ｂの合計面積よりも広く設定することによっても、内輪３の大鍔部３ｃまで至る潤滑油の量を減らすことができ、回転トルクを低減できる。   The lubricating oil flowing from the inner diameter side of the cage 5 to the inner ring 3 side sets the gap δ between the rib tip 5d of the cage 5 and the small flange 3b of the inner ring 3 so that the outer diameter of the cage 5 is reduced. Much less than the lubricating oil flowing from the side, and most of the lubricating oil flowing from the gap δ passes through the notch 6a provided in the narrow column 5c of the pocket 6 and is retained. It moves to the outer diameter side of the vessel 5. Accordingly, the amount of the lubricating oil that reaches the large collar portion 3c along the raceway surface 3a of the inner ring 3 is extremely reduced, and the amount of the lubricating oil staying in the bearing can be reduced, so that the rotational torque can be reduced. In this embodiment, since the notch 6c is provided also in the small annular portion 5a on the narrow side of the pocket 6, the lubricating oil flowing into the inner ring 3 side can be further moved to the outer ring 2 side, and rotational torque Further reduction can be expected. Further, by setting the total area of the notches 6 a and 6 c provided on the narrow side of the pocket 6 to be larger than the total area of the notches 6 b provided on the wide side, the large ring portion 3 c of the inner ring 3 is reached. The amount of lubricating oil can be reduced, and the rotational torque can be reduced.

また、ポケット６の広幅側の柱部５ｃにも切り欠き６ｂを設けられているため、円錐ころ４をバランスよく柱部５ｃに摺接させることができる。   Moreover, since the notch 6b is provided also in the column part 5c of the wide side of the pocket 6, the tapered roller 4 can be slidably contacted with the column part 5c with good balance.

保持器５の表面、特に保持器５の外径面は、できるだけ滑らかな表面にしておくのがよい。すなわち、円錐ころ軸受１の回転中は保持器５外径面の突起部５ｅと外輪軌道面との間に楔状油膜が形成されてその動圧作用で保持器５の外径面の突起部５ｅが外輪軌道面に接触することはないが、円錐ころ軸受１の回転開始直後は低回転数のため、十分な楔状油膜が形成されず、過酷な潤滑条件が発生すると保持器５の外径面の突起部５ｅが外輪軌道面２ａに接触する可能性がある。このような場合に備えて、保持器５の外径面を例えば二硫化モリブデン（ＭＯＳ２）系のコーティング処理をしたり、またはバレル研磨仕上げ等を行なうことにより可及的に摩擦係数を低減する処置をしておくのがよい。 The surface of the cage 5, particularly the outer diameter surface of the cage 5, should be as smooth as possible. That is, during rotation of the tapered roller bearing 1, a wedge-shaped oil film is formed between the protrusion 5e on the outer diameter surface of the cage 5 and the outer raceway surface, and the dynamic pressure action causes the protrusion 5e on the outer diameter surface of the cage 5. Is not in contact with the outer ring raceway surface, but immediately after the rotation of the tapered roller bearing 1 is started, the rotational speed is low, so that a sufficient wedge-shaped oil film is not formed. May be in contact with the outer ring raceway surface 2a. In preparation for such a case, the coefficient of friction is reduced as much as possible by, for example, applying a molybdenum disulfide (MOS 2 ) coating to the outer diameter surface of the cage 5 or performing a barrel polishing finish. It is better to take treatment.

保持器５は鋼板プレス製品のほか、樹脂製としてもよい。樹脂の種類として、自動車トランスミッションでの使用を前提する場合は、耐油性を考慮してＰＰＳ、ＰＥＥＫ、ＰＰＡ等のスーパーエンプラ又はポリアミド樹脂とするのが望ましい。樹脂製の保持器は鋼板プレス製保持器５と比べると重量が軽く摩擦係数が小さいという特徴を有する。   The cage 5 may be made of resin other than a steel plate press product. When the resin is assumed to be used in an automobile transmission, it is desirable to use super engineering plastics such as PPS, PEEK, PPA, or polyamide resin in consideration of oil resistance. The cage made of resin has a feature that it is lighter and has a smaller friction coefficient than the cage 5 made of steel plate press.

本発明の円錐ころ軸受１は以上にように構成されており、軸受１が回転して保持器５が回転し始めると、外輪軌道面２ａと保持器５の突起部５ｅとの間に楔状油膜が形成される。この楔状油膜は軸受１の回転速度にほぼ比例した動圧を発生するので、保持器５のピッチ円直径を大きくして外輪軌道面に近接させても、軸受１を大きな摩耗ないしトルク損失を生じることなく回転させることが可能となり、無理なく円錐ころの本数を増加させることが可能となる。これにより、軌道面の最大面圧が低減され、表面起点剥離による不具合を回避できる。なお、上記のような動圧作用がなくても保持器５を十分に拡径できる場合は、突起部５ｅを設ける必要はない。   The tapered roller bearing 1 of the present invention is configured as described above, and when the bearing 1 rotates and the cage 5 begins to rotate, a wedge-shaped oil film is formed between the outer ring raceway surface 2a and the protrusion 5e of the cage 5. Is formed. Since this wedge-shaped oil film generates a dynamic pressure substantially proportional to the rotational speed of the bearing 1, even if the pitch circle diameter of the cage 5 is increased and brought close to the outer ring raceway surface, the bearing 1 generates a large amount of wear or torque loss. Therefore, the number of tapered rollers can be increased without difficulty. Thereby, the maximum surface pressure of a raceway surface is reduced and the malfunction by surface origin peeling can be avoided. If the cage 5 can be sufficiently expanded even without the dynamic pressure action as described above, it is not necessary to provide the protrusion 5e.

上記のように円錐ころの本数を増やした場合、軸受内部の潤滑油による流動抵抗が増し、回転トルクが増大する恐れがある。この対策として、ポケット６の狭幅側の柱部５ｃ及び小環状部５ａに、切り欠き６ａ、６ｃが設けられることで、円錐ころ軸受１内部の潤滑油の循環が良好になり、軸受内部に滞留する潤滑油の量を減らすことができる。よって、潤滑油の流動抵抗によるトルクが低減される。   When the number of tapered rollers is increased as described above, the flow resistance due to the lubricating oil inside the bearing is increased, which may increase the rotational torque. As a countermeasure, the notch 6a, 6c is provided in the column portion 5c and the small annular portion 5a on the narrow width side of the pocket 6, so that the circulation of the lubricating oil inside the tapered roller bearing 1 is improved, and the inside of the bearing is The amount of lubricating oil that stays can be reduced. Therefore, torque due to the flow resistance of the lubricating oil is reduced.

また、円錐ころの本数を増やすために保持器５を拡径すると、以下のような不具合も生じる。保持器５に円錐ころ４を組付ける際には、保持器５をその小環状部５ａを下向きにした状態で設置し、図６に示すように円錐ころ４をその小径端面４ａを下向きにして上方から降下させ、ポケット６内に内側から挿入する。次に、図７に示すように円錐ころ４の小径端面４ａがポケット６の端縁部に引っ掛かり、その円錐ころ４が径方向外側（矢印で示す方向）に傾倒して、円錐ころ４が保持器５に設置される。保持器５のリブの先端部５ｄを径方向と平行に形成すると、円錐ころ４の小径端面４ａがポケット６の端縁部に引っ掛かる時に、その円錐ころ４は、ポケット６の端縁部のみで支持されることになり、非常に不安定な状態となる。特に、上記のように、保持器５を拡径した場合、円錐ころ４の小径端面４ａがポケット６の端縁部に引っ掛かる部分が小さくなるため、さらに不安定になり、円錐ころ４が円周方向に傾倒するおそれがある。   Further, when the diameter of the cage 5 is increased in order to increase the number of tapered rollers, the following problems also occur. When assembling the tapered roller 4 to the cage 5, the cage 5 is installed with the small annular portion 5a facing downward, and the tapered roller 4 is placed with its small-diameter end surface 4a facing downward as shown in FIG. It is lowered from above and inserted into the pocket 6 from the inside. Next, as shown in FIG. 7, the small-diameter end face 4a of the tapered roller 4 is caught on the edge of the pocket 6, and the tapered roller 4 is tilted radially outward (in the direction indicated by the arrow) to be held by the tapered roller 4. Installed in vessel 5. If the tip 5d of the rib of the cage 5 is formed parallel to the radial direction, when the small diameter end surface 4a of the tapered roller 4 is caught by the edge of the pocket 6, the tapered roller 4 is formed only at the edge of the pocket 6. It will be supported and will be in a very unstable state. In particular, when the diameter of the cage 5 is increased as described above, the portion where the small-diameter end surface 4a of the tapered roller 4 is caught by the edge of the pocket 6 becomes smaller, which makes the tapered roller 4 circumferential. There is a risk of tilting in the direction.

図６、図７に示すように、保持器５のリブの先端部５ｄを軸方向内側に屈曲させた形状とすると、円錐ころ４の小径端面４ａがポケット６に引っ掛かったときに、円錐ころ４が保持器５の小環状部５ａとリブの先端部５ｄとで支持される。これにより、円錐ころ４が安定した姿勢に保持されるため、上記の不具合を回避できる。   As shown in FIGS. 6 and 7, when the tip 5 d of the rib of the cage 5 is bent inward in the axial direction, when the small diameter end surface 4 a of the tapered roller 4 is caught in the pocket 6, the tapered roller 4 Is supported by the small annular portion 5a of the cage 5 and the tip portion 5d of the rib. Thereby, since the tapered roller 4 is hold | maintained in the stable attitude | position, said malfunction can be avoided.

円錐ころ軸受１が以上の構成を有することにより、保持器５を拡径しても、組み付けが効率よく行われ、且つ、回転トルクを低減させることができる。本発明は、上記の実施形態に限定されることなく、種々の変形が可能である。例えば、ポケット６の小環状部５ａの切り欠き６ｃが無くてもトルク低減効果が十分に得られる場合や、ポケット６の広幅側の柱部５ｃの切り欠き６ｂが無くても円錐ころがバランスよく柱部５ｃに摺接することができる場合は、これらを省略することができる。   Since the tapered roller bearing 1 has the above-described configuration, the assembly can be efficiently performed and the rotational torque can be reduced even if the diameter of the cage 5 is increased. The present invention is not limited to the above-described embodiment, and various modifications can be made. For example, when the torque reduction effect can be sufficiently obtained without the notch 6c of the small annular portion 5a of the pocket 6, or when the notch 6b of the column portion 5c on the wide side of the pocket 6 is not provided, the tapered roller is well balanced. These can be omitted when they can be slidably contacted with the column part 5c.

次に、以上に説明した円錐ころ軸受１を自動車のトランスミッションに適用し、その一実施形態を図８に基いて説明する。   Next, the tapered roller bearing 1 described above is applied to an automobile transmission, and an embodiment thereof will be described with reference to FIG.

図８は、自動車 のトランスミッションの一構成例を示している。このトランスミッシ
ョンは同期噛合式のもので、同図で左方向がエンジン側、右方向が駆動車輪側である。メインシャフト１１とメインドライブギヤ１２との間に、本発明の円錐ころ軸受１が介装される。この例では、メインドライブギヤ１２の内周に円錐ころ軸受１の外輪軌道面が直接形成されている。メインドライブギヤ１２は、別の円錐ころ軸受１でケーシング１３に対して回転自在に支持される。メインドライブギヤ１２にクラッチギヤ１４が係合連結され、クラッチギヤ１４に近接してシンクロ機構１５が配設される。 FIG. 8 shows an example of the configuration of a vehicle transmission. This transmission is of a synchronous mesh type, and in the figure the left direction is the engine side and the right direction is the drive wheel side. The tapered roller bearing 1 of the present invention is interposed between the main shaft 11 and the main drive gear 12. In this example, the outer ring raceway surface of the tapered roller bearing 1 is directly formed on the inner periphery of the main drive gear 12. The main drive gear 12 is rotatably supported with respect to the casing 13 by another tapered roller bearing 1. A clutch gear 14 is engaged and connected to the main drive gear 12, and a synchronization mechanism 15 is disposed in the vicinity of the clutch gear 14.

シンクロ機構１５は、セレクタ（図示省略）の作動によって軸方向（同図で左右方向）に移動するスリーブ１６と、スリーブ１６の内周に軸方向移動自在に装着されたシンクロナイザーキー１７と、メインシャフト１１の外周に係合連結されたハブ１８と、クラッチギヤ１４の外周（コーン部）に摺動自在に装着されたシンクロナイザーリング１９と、シンクロナイザーキー１７をスリーブ１６の内周に弾性的に押圧する押さえピン２０及びスプリング２１とを備えている。   The synchronizer 15 includes a sleeve 16 that moves in the axial direction (left and right in the figure) by the operation of a selector (not shown), a synchronizer key 17 that is mounted on the inner periphery of the sleeve 16 so as to be axially movable, A hub 18 engaged and connected to the outer periphery of the shaft 11, a synchronizer ring 19 slidably mounted on the outer periphery (cone portion) of the clutch gear 14, and a synchronizer key 17 are elastically attached to the inner periphery of the sleeve 16. A pressing pin 20 and a spring 21 are provided.

同図に示す状態では、スリーブ１６及びシンクロナイザーキー１７が押さえピン２０によって中立位置に保持されている。この時、メインドライブギヤ１２はメインシャフト１１に対して空転する。一方、セレクタの作動により、スリーブ１６が同図に示す状態から例えば軸方向左側に移動すると、スリーブ１６に従動してシンクロナイザーキー１７が軸方向左側に移動し、シンクロナイザーリング１９をクラッチギヤ１４のコーン部の傾斜面に押し付ける。これにより、クラッチギヤ１４の回転速度が落ち、逆にシンクロ機構１５側の回転速度が高められる。そして、両者の回転速度が同期した頃、スリーブ１６がさらに軸方向左側に移動して、クラッチギヤ１４と噛み合い、メインシャフト１１とメインドライブギヤ１２との間がシンクロ機構１５を介して連結される。これにより、メインシャフト１１とメインドライブギヤ１２とが同期回転する。   In the state shown in the figure, the sleeve 16 and the synchronizer key 17 are held in the neutral position by the pressing pin 20. At this time, the main drive gear 12 idles with respect to the main shaft 11. On the other hand, when the sleeve 16 is moved to the left side in the axial direction from the state shown in the figure by the operation of the selector, the synchronizer key 17 is moved to the left side in the axial direction following the sleeve 16 and the synchronizer ring 19 is moved to the clutch gear 14. Press against the inclined surface of the cone. Thereby, the rotational speed of the clutch gear 14 falls, and conversely, the rotational speed on the synchro mechanism 15 side is increased. When the rotational speeds of the two are synchronized, the sleeve 16 further moves to the left in the axial direction, meshes with the clutch gear 14, and the main shaft 11 and the main drive gear 12 are connected via the sync mechanism 15. . Thereby, the main shaft 11 and the main drive gear 12 rotate synchronously.

本発明に係る円錐ころ軸受１ は、上記のように自動車のトランスミッションに組み込む他、自動車のデファレンシャルや、自動車用歯車装置以外の用途に使用することも可能である。   The tapered roller bearing 1 according to the present invention can be used for applications other than automobile differentials and automobile gears, in addition to being incorporated in automobile transmissions as described above.

本発明に係る円錐ころ軸受１の断面図である。1 is a cross-sectional view of a tapered roller bearing 1 according to the present invention. 本発明に係る円錐ころ軸受１の部分断面図である。1 is a partial cross-sectional view of a tapered roller bearing 1 according to the present invention. 保持器５の部分斜視図である。It is a fragmentary perspective view of the holder | retainer 5. FIG. 保持器５の柱部５ｃの断面図である。It is sectional drawing of the pillar part 5c of the holder | retainer 5. FIG. 円錐ころ軸受１の軸受内部への潤滑油の流れを示す断面図である。3 is a cross-sectional view showing the flow of lubricating oil into the bearing of the tapered roller bearing 1. FIG. 保持器５に円錐ころ４を挿入する要領を説明するための断面図である。It is sectional drawing for demonstrating the point which inserts the tapered roller 4 in the holder | retainer 5. FIG. 保持器５に円錐ころ４を挿入する要領を説明するための断面図である。It is sectional drawing for demonstrating the point which inserts the tapered roller 4 in the holder | retainer 5. FIG. 自動車のトランスミッションの部分断面図である。It is a fragmentary sectional view of the transmission of a car.

符号の説明Explanation of symbols

１ 円錐ころ軸受
２ 外輪
３ 内輪
４ 円錐ころ
５ 保持器
５ａ 小環状部
５ｂ 大環状部
５ｃ 柱部
５ｄ リブ先端部
５ｅ 突起部
６ ポケット
６ａ、６ｂ、６ｃ 切り欠き DESCRIPTION OF SYMBOLS 1 Tapered roller bearing 2 Outer ring 3 Inner ring 4 Tapered roller 5 Cage 5a Small annular part 5b Large annular part 5c Column part 5d Rib tip part 5e Protrusion part 6 Pocket 6a, 6b, 6c Notch

Claims (4)

内輪と、外輪と、前記内輪と外輪との間に転動自在に配された複数の円錐ころと、前記円錐ころを円周所定間隔に収納するポケットを有する保持器とを備え、前記保持器が、前記円錐ころの小径側で連なる小環状部と、円錐ころの大径側で連なる大環状部と、これらの環状部を連結する複数の柱部とからなり、前記ポケットが、前記円錐ころの小径側を収納する部分が狭幅側、大径側を収納する部分が広幅側となる台形状に形成された円錐ころ軸受において、
前記保持器の小環状部の端縁から径方向にリブを延在させ、そのリブの先端部を軸方向内側に屈曲させた形状とし、且つ、前記保持器の台形状ポケットの狭幅側の柱部に切り欠きを設けたことを特徴とする円錐ころ軸受 。 An inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and a cage having a pocket for accommodating the tapered rollers at predetermined circumferential intervals, Is composed of a small annular portion that is continuous on the small diameter side of the tapered roller, a large annular portion that is continuous on the large diameter side of the tapered roller, and a plurality of column portions that connect these annular portions, and the pocket is the tapered roller In the tapered roller bearing formed in a trapezoidal shape in which the portion storing the small diameter side is the narrow side and the portion storing the large diameter side is the wide side,
A rib is extended in the radial direction from the edge of the small annular portion of the cage, the tip of the rib is bent inward in the axial direction, and the narrow side of the trapezoidal pocket of the cage A tapered roller bearing characterized in that a notch is provided in a column part. 前記台形状ポケットの狭幅側の小環状部にも切欠きを設けた請求項１記載の円錐ころ軸受 。   The tapered roller bearing according to claim 1, wherein a notch is provided in a small annular portion on a narrow side of the trapezoidal pocket. 前記台形状ポケットの広幅側の少なくとも柱部に切り欠きを設けた請求項１記載の円錐ころ軸受 。   The tapered roller bearing according to claim 1, wherein a notch is provided in at least a column part on the wide side of the trapezoidal pocket. 前記台形状ポケットの狭幅側に設けた切り欠きの合計面積を、前記台形状ポケットの広幅側に設けた切り欠きの合計面積よりも広くした請求項１記載の円錐ころ軸受。   The tapered roller bearing according to claim 1, wherein a total area of notches provided on the narrow side of the trapezoidal pocket is wider than a total area of notches provided on the wide side of the trapezoidal pocket.
JP2005270349A 2005-09-16 2005-09-16 Tapered roller bearing and assembly method thereof Expired - Fee Related JP4823624B2 (en)

Priority Applications (2)

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JP2005270349A JP4823624B2 (en) 2005-09-16 2005-09-16 Tapered roller bearing and assembly method thereof
PCT/JP2006/318353 WO2007032470A1 (en) 2005-09-16 2006-09-15 Conical roller bearing

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007085526A (en) * 2005-09-26 2007-04-05 Ntn Corp Conical roller bearing
WO2017033977A1 (en) * 2015-08-27 2017-03-02 Ntn株式会社 Holder and tapered roller bearing
JP2020112269A (en) * 2020-04-20 2020-07-27 Ntn株式会社 Cage and conical roller bearing

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JPS50126841A (en) * 1974-03-29 1975-10-06
JPS5593727A (en) * 1978-12-29 1980-07-16 Seiichi Tatsumi Product sorting device
JPH11101240A (en) * 1997-09-26 1999-04-13 Ntn Corp Holder for conical roller bearing and manufacture thereof
JPH11201149A (en) * 1998-01-12 1999-07-27 Koyo Seiko Co Ltd Tapered roller bearing
JP2005098412A (en) * 2003-09-25 2005-04-14 Koyo Seiko Co Ltd Tapered roller bearing

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50126841A (en) * 1974-03-29 1975-10-06
JPS5593727A (en) * 1978-12-29 1980-07-16 Seiichi Tatsumi Product sorting device
JPH11101240A (en) * 1997-09-26 1999-04-13 Ntn Corp Holder for conical roller bearing and manufacture thereof
JPH11201149A (en) * 1998-01-12 1999-07-27 Koyo Seiko Co Ltd Tapered roller bearing
JP2005098412A (en) * 2003-09-25 2005-04-14 Koyo Seiko Co Ltd Tapered roller bearing

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007085526A (en) * 2005-09-26 2007-04-05 Ntn Corp Conical roller bearing
WO2017033977A1 (en) * 2015-08-27 2017-03-02 Ntn株式会社 Holder and tapered roller bearing
JP2017044281A (en) * 2015-08-27 2017-03-02 Ntn株式会社 Cage and conical roller bearing
CN107923440A (en) * 2015-08-27 2018-04-17 Ntn株式会社 Retainer and taper roll bearing
US10330146B2 (en) 2015-08-27 2019-06-25 Ntn Corporation Retainer and tapered roller bearing
CN107923440B (en) * 2015-08-27 2020-06-26 Ntn株式会社 Retainer and tapered roller bearing
JP2020112269A (en) * 2020-04-20 2020-07-27 Ntn株式会社 Cage and conical roller bearing
JP7072017B2 (en) 2020-04-20 2022-05-19 Ntn株式会社 Cage and tapered roller bearings

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