JP4069616B2 - Bearing device for pinion shaft support - Google Patents

Bearing device for pinion shaft support Download PDF

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Publication number
JP4069616B2
JP4069616B2 JP2001366070A JP2001366070A JP4069616B2 JP 4069616 B2 JP4069616 B2 JP 4069616B2 JP 2001366070 A JP2001366070 A JP 2001366070A JP 2001366070 A JP2001366070 A JP 2001366070A JP 4069616 B2 JP4069616 B2 JP 4069616B2
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Prior art keywords
bearing
pinion shaft
thrust
pinion
pinion gear
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Expired - Fee Related
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JP2001366070A
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JP2003166626A (en
Inventor
章之 鈴木
寛一 耕田
博文 百々路
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JTEKT Corp
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JTEKT Corp
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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/545—Systems comprising at least one rolling bearing for radial load in combination with at least one rolling bearing for axial load
    • 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
    • F16C19/49—Bearings with both balls and rollers
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • 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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement

Abstract

<P>PROBLEM TO BE SOLVED: To improve the efficiency of a differential gear by reducing turning torque, in a pinion shaft supporting bearing device for supporting a pinion shaft 4 constituting an automotive differential gear in a rotatable relation in a differential case 1. <P>SOLUTION: The bearing device supports the pinion shaft 4 in a rotatable relation to the differential case 1. A pinion gear side rolling bearing 6 comprises a deep groove ball bearing 61 and a thrust ball bearing 62 juxtaposed axially. A pair of rolling bearings 5 and 6 are fixed to the differential case 1 by coupling of a companion flange 7 in the pinion gear direction by means of a nut 15. <P>COPYRIGHT: (C)2003,JPO

Description

【０００１】
【発明の属する技術分野】
本発明は、自動車のディファレンシャル装置を構成するピニオン軸を、ディファレンシャルケースの内側に回転自在に支持するためのピニオン軸支持用軸受装置に関する。
【０００２】
【従来の技術】
従来のディファレンシャル装置の構造を図５に示す。
【０００３】
図５において、１はディファレンシャルケースであり、このディファレンシャルケース１内に、左右の車輪を差動連動する差動変速機構２、ピニオンギヤ３、ピニオン軸４、ピニオン軸４を回転自在に支持する円すいころ軸受５０，６０等が収納されている。
【０００４】
ピニオンギヤ３は、差動変速機構２のリングギヤ２ａに噛合されており、ピニオン軸４の内端部に一体形成されている。
【０００５】
また、ピニオン軸４は、背面合わせに配置した単列の円すいころ軸受５０，６０にて、ディファレンシャルケース１の内側に回転自在に支持されており、外端部にはドライブシャフト（図示せず）が連結されるコンパニオンフランジ７が設けられている。
【０００６】
また、円すいころ軸受５０，６０は、各々ディファレンシャルケース１の鍛造製の軸受ケース部１ａに形成した軸受装着用の環状壁１３，１４の内周面に装着されている。なお、コンパニオンフランジ側の円すいころ軸受５０は軸受ケース部１ａの小径側開口部から組み込まれ、ピニオンギヤ側の円すいころ軸受６０は軸受ケース部１ａの大径側開口部から組み込まれ、両円すいころ軸受５０，６０間には位置決め用のスペーサ８が介装されている。円すいころ軸受５０，６０は、ピニオン軸４の外端部にナット１５を螺合し、コンパニオンフランジ７に締結することで、ピニオンギヤ３とコンパニオンフランジ７の間で十分な予圧を付与して固定される。
【０００７】
さらに、ディファレンシャルケース１内には、潤滑用のオイルが運転停止状態においてレベルＬにて貯留されている。オイルは、運転時にリングギヤ２ａの回転に伴って跳ね上げられ、軸受ケース部１ａ内の環状壁１３，１４間に形成したオイル導入路１１を通って円すいころ軸受５０，６０に導かれ、さらにオイル還流路（図示せず）を通って戻される。なお、ピニオン軸４の外端部側の外周面と軸受ケース部１ａの内周面との間には、オイルの漏洩防止のためのオイルシール９が装着されており、かつ、オイルシール９を隠蔽するシール保護カップ１０が取付けられている。
【０００８】
【発明が解決しようとする課題】
従来のディファレンシャル装置の場合、ピニオン軸４を回転自在に支持する軸受が円すいころ軸受５０，６０からなり、特に、スラスト荷重の大きなピニオンギヤ側の円すいころ軸受６０には大きな摩擦抵抗が作用するので、回転トルクが大きくなり、ディファレンシャル装置の効率が低下するという問題があった。
【０００９】
この発明は、回転トルクが小さくなり、ディファレンシャル装置の効率が向上するピニオン軸支持用軸受装置を提供することを目的とする。
【００１０】
【課題を解決するための手段】
本発明は、ピニオン軸の一端に設けたピニオンギヤと、他端に設けたコンパニオンフランジとの間に、前記ピニオン軸をディファレンシャルケースに対して回転自在に支持する軸心方向に並設した一対の転がり軸受を装着してなるピニオン軸支持用軸受装置であって、ピニオンギヤ側の転がり軸受は、深溝玉軸受とスラスト軸受を軸心方向に並設し、かつ、前記スラスト軸受を前記深溝玉軸受よりピニオンギヤ側に配置してなり、前記スラスト軸受は一対の軌道輪の間に転動体を介装してなり、一方の軌道輪が前記ピニオンギヤの背面に圧接されて前記ピニオン軸に圧入固定され、他方の軌道輪が前記ピニオン軸との間に隙間を介して前記ディファレンシャルケースの軸受ケース部に圧入固定され、前記深溝玉軸受は内輪と外輪の間に玉を介装してなり、前記内輪が前記スラスト軸受の他方の軌道輪との間に隙間を介して前記ピニオン軸に圧入固定され、前記外輪が前記スラスト軸受の他方の軌道輪に圧接されて前記ディファレンシャルケースの軸受ケース部に圧入固定され、前記コンパニオンフランジを締結手段にて前記ピニオンギヤ方向に締結することにより前記一対の転がり軸受を前記ディファレンシャルケースの軸受ケース部に固定したことを特徴とするものである。
【００１１】
なお、ピニオンギヤ側の転がり軸受のスラスト軸受には、例えば、スラスト針状ころ軸受またはスラスト玉軸受を用いる。
【００１２】
本発明のピニオン軸支持用軸受装置によると、大きなスラスト荷重が作用するピニオンギヤ側の転がり軸受を深溝玉軸受とスラスト軸受を軸心方向に並設して構成し、これら円すいころ軸受に比べて摩擦抵抗の小さい深溝玉軸受、ならびにスラスト針状ころ軸受またはスラスト玉軸受からなるスラスト軸受にて、ラジアル荷重ならびにアキシアル荷重を受けるので、円すいころ軸受に比べて回転トルクが小さくなり、ディファレンシャル装置の効率が向上する。
【００１３】
また、ピニオンギヤ側の転がり軸受のスラスト軸受を深溝玉軸受よりピニオンギヤ側に配置し、かつ、前記スラスト軸受をピニオンギヤの背面に設けたことで、スラスト軸受にてアキシアル荷重を直接受けることができ、モーメントが小さくなり、軸受の小型化ならびに低トルク化が図れる。
【００１５】
【発明の実施の形態】
（実施の形態１）
本発明の実施の形態１について、図１および図２を用いて説明する。
【００１６】
図１は、実施の形態１におけるピニオン軸支持用軸受装置を適用したディファレンシャル装置の断面図、図２は、ピニオン軸支持用軸受装置の部分断面図を示している。
【００１７】
実施の形態１のピニオン軸支持用軸受装置は、コンパニオンフランジ側の転がり軸受５がアンギュラ玉軸受からなり、ピニオンギヤ側の転がり軸受６が深溝玉軸受６１とスラスト玉軸受６２を、スラスト玉軸受６２が深溝玉軸受６１よりピニオンギヤ側になるように並設してなることを特徴とするものである。
【００１８】
なお、その他の構成は図５の例と略同一であり、同一部分には同一符号を付してその説明を省略する。
【００１９】
すなわち、コンパニオンフランジ側の転がり軸受５のアンギュラ玉軸受は、内輪５１、外輪５２、保持器にて保持された玉群５３からなる。
【００２０】
また、ピニオンギヤ側の転がり軸受６の深溝玉軸受６１は、内輪６３、外輪６４、保持器にて保持された玉群６５からなり、スラスト玉軸受６２は、一対の軌道輪６６，６７と保持器にて保持された玉群６８からなる。
【００２１】
なお、ピニオンギヤ側の転がり軸受６にはコンパニオンフランジ側の転がり軸受５に比べて大きなスラスト荷重が作用するため、深溝玉軸受６１は負荷容量の大きな軸受、すなわち転がり軸受５に比べて外径寸法が大きく、ラジアル荷重を確実に受けることができる軸受を用いる。
【００２２】
スラスト玉軸受６２の一方の軌道輪６６は、ピニオンギヤ３の背面に圧接されてピニオン軸４に圧入され、他方の軌道輪６７は、ピニオン軸４との間に隙間を介して環状壁１４に圧入される。
【００２３】
また、深溝玉軸受６１の内輪６３は、スラスト玉軸受６２の軌道輪６７との間に隙間を介してピニオン軸４に圧入され、外輪６４は軌道輪６７に圧接されて環状壁１４に圧入される。
【００２４】
転がり軸受６は、深溝玉軸受６１とスラスト玉軸受６２が並設された状態で、スラスト玉軸受６２の軌道輪６６ならびに深溝玉軸受６１の内輪６３をピニオン軸４に圧入すると共に、軸受ケース部１ａの大径側開口部から組み込まれて、深溝玉軸受６１の外輪６４ならびにスラスト玉軸受６２の軌道輪６７を環状壁１４に圧入する。
【００２５】
また、転がり軸受５は、内輪５１をピニオン軸４に圧入すると共に、外輪５2を環状壁１３に圧入する。
【００２６】
さらに、コンパニオンフランジ７をピニオン軸４のドライブシャフト側の小径部４４にスプライン嵌合し、締結手段となるナット１５をコンパニオンフランジ７に締結する。これにより、転がり軸受５，６が、ピニオンギヤ３とコンパニオンフランジ７にて挟み込まれて軸受ケース部１ａに固定される。
【００２７】
このようにして、深溝玉軸受６１にてラジアル荷重を受け、かつ、スラスト玉軸受６２にてアキシアル荷重を受けると共に、転がり軸受５にてラジアル荷重ならびにアキシアル荷重を受けて、ピニオン軸４をディファレンシャルケース１に対して回転自在に支持する。
【００２８】
このように構成されたピニオン軸支持用軸受装置によると、大きなスラスト荷重が作用するピニオンギヤ側の転がり軸受６を深溝玉軸受６１とスラスト玉軸受６２を軸心方向に並設して構成し、これら円すいころ軸受に比べて摩擦抵抗の小さい深溝玉軸受６１ならびにスラスト玉軸受６２にて、ラジアル荷重ならびにアキシアル荷重を受けるので、円すいころ軸受に比べて回転トルクが小さくなり、ディファレンシャル装置の効率が向上する。
【００２９】
同様に、コンパニオンフランジ側の転がり軸受５においても、円すいころ軸受に比べて摩擦抵抗の小さいアンギュラ玉軸受にて、ラジアル荷重ならびにアキシアル荷重を受けるので、円すいころ軸受に比べて回転トルクが小さくなり、ディファレンシャル装置の効率がより一層向上する。
【００３０】
また、スラスト玉軸受６２をピニオンギヤ３の背面に設け、アキシアル荷重を直接受ける構造としたので、モーメントが小さくなり、軸受の小型化ならびに低トルク化が図れる。
【００３１】
なお、締結手段は、ピニオン軸４のドライブシャフト側端面を外向きにかしめてなるかしめによってもよい。
【００３２】
図３に、実施の形態１におけるピニオン軸支持用軸受装置の変形例を示す。
【００３３】
この変形例は、深溝玉軸受６１とスラスト玉軸受６２を並設してなるピニオンギヤ側の転がり軸受６において、スラスト玉軸受６２の軌道輪６６，６７の幅寸法を小さくし、深溝玉軸受６１の外輪６４とピニオンギヤ３の間に圧入したことを特徴とするものである。
【００３４】
なお、その他の構成は図１および図２に示した例と同様である。
（実施の形態２）
本発明の実施の形態２について、図４を用いて説明する。
【００３５】
図４は、実施の形態２におけるピニオン軸支持用軸受装置の部分断面図を示している。
【００３６】
この実施の形態２は、コンパニオンフランジ側の転がり軸受５がアンギュラ玉軸受からなり、ピニオンギヤ側の転がり軸受６が深溝玉軸受６１とスラスト針状ころ軸受７１を、スラスト針状ころ軸受７１が深溝玉軸受６１よりピニオンギヤ側になるように並設してなることを特徴とするものである。なお、その他の構成は、実施の形態１と同様である。
【００３７】
すなわち、コンパニオンフランジ側の転がり軸受５ならびにピニオンギヤ側の転がり軸受６の深溝玉軸受６１は、実施の形態１と同様に構成されている。また、スラスト針状ころ軸受７１は、一対の軌道輪７２，７３、保持器７５にて保持された針状ころ群７４からなる。
【００３８】
スラスト針状ころ軸受７１の一方の軌道輪７２は、ピニオンギヤ３の背面に圧接されてピニオン軸４に圧入され、他方の軌道輪７３は、ピニオン軸４との間に隙間を介して環状壁１４に圧入される。
【００３９】
また、深溝玉軸受６１の内輪６３は、スラスト針状ころ軸受７１の軌道輪７３との間に隙間を介してピニオン軸４に圧入され、外輪６４は軌道輪７３に圧接されて環状壁１４に圧入される。
【００４０】
転がり軸受６は、深溝玉軸受６１とスラスト針状ころ軸受７１が並設された状態で、スラスト針状ころ軸受７１の軌道輪７２ならびに深溝玉軸受６１の内輪６３をピニオン軸４に圧入すると共に、軸受ケース部１ａの大径側開口部から組み込まれて、深溝玉軸受６１の外輪６４ならびにスラスト針状ころ軸受７１の軌道輪７３を環状壁１４に圧入する。
【００４１】
また、転がり軸受５は、内輪５１をピニオン軸４に圧入すると共に、外輪５2を環状壁１３に圧入する。
【００４２】
さらに、コンパニオンフランジ７をピニオン軸４のドライブシャフト側の小径部４４にスプライン嵌合し、締結手段となるナット１５をコンパニオンフランジ７に締結する。これにより、転がり軸受５，６が、ピニオンギヤ３とコンパニオンフランジ７にて挟み込まれて軸受ケース部１ａに固定される。
【００４３】
このようにして、深溝玉軸受６１にてラジアル荷重を受け、かつ、スラスト針状ころ軸受７１にてアキシアル荷重を受けると共に、転がり軸受５にてラジアル荷重ならびにアキシアル荷重を受けて、ピニオン軸４をディファレンシャルケース１に対して回転自在に支持する。
【００４４】
このように構成されたピニオン軸支持用軸受装置においても、実施の形態１と同様の効果が得られる。
【００４５】
なお、ピニオンギヤ側の転がり軸受６において、深溝玉軸受６１をスラスト軸受６２，７１よりピニオンギヤ３側に設けてもよい。
【００４６】
また、スラスト玉軸受６２，スラスト針状ころ軸受７１は、スラスト軸受の一例であり、これに限定されるものではなく、スラスト円筒ころ軸受等、各種スラスト軸受を用いることができる。
【００４７】
さらに、各実施の形態において、コンパニオンフランジ側の転がり軸受５は、アンギュラ玉軸受からなるものであったが、これに限るものではなく、例えば、図５に示した円すいころ軸受や、各種ラジアル軸受とスラスト軸受の組合せにて構成してもよい。
【００４８】
【発明の効果】
本発明のピニオン軸支持用軸受装置によれば、回転トルクが小さくなり、ディファレンシャル装置の効率が向上するという効果が得られる。
【図面の簡単な説明】
【図１】本発明の実施の形態１におけるピニオン軸支持用軸受装置を適用したディファレンシャル装置の断面図である。
【図２】本発明の実施の形態１におけるピニオン軸支持用軸受装置の部分断面図である。
【図３】本発明の実施の形態１におけるピニオン軸支持用軸受装置の変形例の部分断面図である。
【図４】本発明の実施の形態２におけるピニオン軸支持用軸受装置の部分断面図である。
【図５】従来例におけるディファレンシャル装置の断面図である。
【符号の説明】
１ ディファレンシャルケース
２ 差動変速機構
２ａ リングギヤ
３ ピニオンギヤ
４ ピニオン軸
５ コンパニオンフランジ側の転がり軸受
６ ピニオンギヤ側の転がり軸受
７ コンパニオンフランジ
１５ ナット（締結手段）
６１ 深溝玉軸受
６２ スラスト玉軸受
７１ スラスト針状ころ軸受[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pinion shaft support bearing device for rotatably supporting a pinion shaft constituting a differential device of an automobile inside a differential case.
[0002]
[Prior art]
The structure of a conventional differential device is shown in FIG.
[0003]
In FIG. 5, reference numeral 1 denotes a differential case, and a tapered roller that rotatably supports a differential transmission mechanism 2, a pinion gear 3, a pinion shaft 4, and a pinion shaft 4 that differentially interlocks the left and right wheels in the differential case 1. Bearings 50 and 60 are accommodated.
[0004]
The pinion gear 3 is meshed with the ring gear 2 a of the differential transmission mechanism 2 and is integrally formed with the inner end portion of the pinion shaft 4.
[0005]
The pinion shaft 4 is rotatably supported inside the differential case 1 by single-row tapered roller bearings 50, 60 arranged back to back, and a drive shaft (not shown) is provided at the outer end. Are connected to each other.
[0006]
Further, the tapered roller bearings 50 and 60 are mounted on inner peripheral surfaces of bearing-mounting annular walls 13 and 14 formed in a forged bearing case portion 1a of the differential case 1, respectively. The tapered roller bearing 50 on the companion flange side is incorporated from the small-diameter side opening of the bearing case 1a, and the tapered roller bearing 60 on the pinion gear side is incorporated from the large-diameter side opening of the bearing case 1a. A positioning spacer 8 is interposed between 50 and 60. The tapered roller bearings 50 and 60 are fixed by applying a sufficient preload between the pinion gear 3 and the companion flange 7 by screwing a nut 15 to the outer end of the pinion shaft 4 and fastening the nut 15 to the companion flange 7. The
[0007]
Further, in the differential case 1, lubricating oil is stored at a level L when the operation is stopped. The oil is sprung up along with the rotation of the ring gear 2a during operation, and is guided to the tapered roller bearings 50 and 60 through the oil introduction path 11 formed between the annular walls 13 and 14 in the bearing case portion 1a. Returned through a reflux path (not shown). An oil seal 9 for preventing oil leakage is mounted between the outer peripheral surface on the outer end side of the pinion shaft 4 and the inner peripheral surface of the bearing case portion 1a. A concealing seal protection cup 10 is attached.
[0008]
[Problems to be solved by the invention]
In the case of the conventional differential device, the bearing that rotatably supports the pinion shaft 4 is composed of tapered roller bearings 50 and 60, and in particular, a large frictional resistance acts on the tapered roller bearing 60 on the pinion gear side having a large thrust load. There has been a problem that the rotational torque is increased and the efficiency of the differential device is reduced.
[0009]
An object of the present invention is to provide a pinion shaft support bearing device in which the rotational torque is reduced and the efficiency of the differential device is improved.
[0010]
[Means for Solving the Problems]
The present invention provides a pair of rolling elements in which a pinion shaft provided at one end of a pinion shaft and a companion flange provided at the other end are juxtaposed in an axial direction to rotatably support the pinion shaft with respect to a differential case. A pinion shaft supporting bearing device having a bearing mounted thereon, the rolling bearing on the pinion gear side includes a deep groove ball bearing and a thrust bearing arranged in parallel in the axial direction, and the thrust bearing is pinned from the deep groove ball bearing. The thrust bearing has a rolling element interposed between a pair of race rings, and one race ring is press-fitted and fixed to the pinion shaft by being pressed against the back surface of the pinion gear. the races through the gap between the pinion shaft is press-fitted into a bearing casing of the differential case, the deep groove ball bearing through the ball between the inner and outer rings And it will be, the inner ring is press-fitted to the pinion shaft through the gap between the other race of the thrust bearing, of the differential case the outer ring is pressed against the other bearing ring of the thrust bearing The pair of rolling bearings are fixed to the bearing case portion of the differential case by being press-fitted and fixed to the bearing case portion and fastening the companion flange in the pinion gear direction by fastening means.
[0011]
Note that, for example, a thrust needle roller bearing or a thrust ball bearing is used as the thrust bearing of the pinion gear side rolling bearing.
[0012]
According to the pinion shaft supporting bearing device of the present invention, the rolling bearing on the pinion gear side on which a large thrust load acts is configured by arranging the deep groove ball bearing and the thrust bearing side by side in the axial direction, and friction compared to these tapered roller bearings. A radial groove and an axial load are applied to a deep groove ball bearing with low resistance and a thrust needle roller bearing or a thrust ball bearing, so the rotational torque is smaller than that of a tapered roller bearing, and the efficiency of the differential device is reduced. improves.
[0013]
Also , the thrust bearing of the rolling bearing on the pinion gear side is arranged on the pinion gear side from the deep groove ball bearing, and the thrust bearing is provided on the back surface of the pinion gear, so that the axial load can be directly received by the thrust bearing, and the moment As a result, the bearing can be reduced in size and torque.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
(Embodiment 1)
Embodiment 1 of the present invention will be described with reference to FIG. 1 and FIG.
[0016]
FIG. 1 is a cross-sectional view of a differential device to which the pinion shaft support bearing device according to the first embodiment is applied, and FIG. 2 is a partial cross-sectional view of the pinion shaft support bearing device.
[0017]
In the bearing device for pinion shaft support according to the first embodiment, the rolling bearing 5 on the companion flange side is an angular ball bearing, the rolling bearing 6 on the pinion gear side is the deep groove ball bearing 61 and the thrust ball bearing 62, and the thrust ball bearing 62 is The deep groove ball bearings 61 are arranged side by side so as to be closer to the pinion gear side.
[0018]
Other configurations are substantially the same as those in the example of FIG. 5, and the same portions are denoted by the same reference numerals and description thereof is omitted.
[0019]
That is, the angular ball bearing of the rolling bearing 5 on the companion flange side includes an inner ring 51, an outer ring 52, and a ball group 53 held by a cage.
[0020]
The deep groove ball bearing 61 of the pinion gear side rolling bearing 6 includes an inner ring 63, an outer ring 64, and a ball group 65 held by a cage, and the thrust ball bearing 62 includes a pair of race rings 66 and 67 and a cage. It consists of a group of balls 68 held at.
[0021]
Since the pinion gear side rolling bearing 6 is subjected to a larger thrust load than the companion flange side rolling bearing 5, the deep groove ball bearing 61 has a larger load capacity, that is, the outer diameter dimension than that of the rolling bearing 5. Use a large bearing that can reliably receive a radial load.
[0022]
One bearing ring 66 of the thrust ball bearing 62 is pressed against the back surface of the pinion gear 3 and is press-fitted into the pinion shaft 4, and the other bearing ring 67 is press-fitted into the annular wall 14 through a gap between the pinion shaft 4. Is done.
[0023]
The inner ring 63 of the deep groove ball bearing 61 is press-fitted into the pinion shaft 4 through a gap between the inner ring 63 and the bearing ring 67 of the thrust ball bearing 62, and the outer ring 64 is pressed into the annular wall 14 while being pressed into the ring ring 67. The
[0024]
The rolling bearing 6 press-fits the race ring 66 of the thrust ball bearing 62 and the inner ring 63 of the deep groove ball bearing 61 into the pinion shaft 4 in a state where the deep groove ball bearing 61 and the thrust ball bearing 62 are juxtaposed, and a bearing case portion. The outer ring 64 of the deep groove ball bearing 61 and the race ring 67 of the thrust ball bearing 62 are press-fitted into the annular wall 14 by being incorporated from the large-diameter side opening of 1a.
[0025]
The rolling bearing 5 presses the inner ring 51 into the pinion shaft 4 and presses the outer ring 52 into the annular wall 13.
[0026]
Further, the companion flange 7 is spline-fitted to the small diameter portion 44 on the drive shaft side of the pinion shaft 4, and the nut 15 serving as a fastening means is fastened to the companion flange 7. As a result, the rolling bearings 5 and 6 are sandwiched between the pinion gear 3 and the companion flange 7 and fixed to the bearing case portion 1a.
[0027]
In this way, the deep groove ball bearing 61 receives a radial load, the thrust ball bearing 62 receives an axial load, and the rolling bearing 5 receives a radial load and an axial load, so that the pinion shaft 4 is subjected to a differential case. 1 is supported rotatably.
[0028]
According to the pinion shaft support bearing device configured as described above, the pinion gear side rolling bearing 6 on which a large thrust load acts is configured by arranging the deep groove ball bearing 61 and the thrust ball bearing 62 in parallel in the axial direction. Since the deep groove ball bearing 61 and the thrust ball bearing 62, which have a smaller frictional resistance than the tapered roller bearing, receive a radial load and an axial load, the rotational torque is smaller than that of the tapered roller bearing, and the efficiency of the differential device is improved. .
[0029]
Similarly, in the rolling bearing 5 on the companion flange side, since the radial ball bearing and the axial load are received by the angular ball bearing having a smaller frictional resistance than the tapered roller bearing, the rotational torque is smaller than that of the tapered roller bearing. The efficiency of the differential device is further improved.
[0030]
Further, since the thrust ball bearing 62 is provided on the back surface of the pinion gear 3 and directly receives the axial load, the moment is reduced, and the bearing can be reduced in size and torque.
[0031]
The fastening means may be caulked by caulking the end surface on the drive shaft side of the pinion shaft 4 outward.
[0032]
FIG. 3 shows a modification of the pinion shaft support bearing device according to the first embodiment.
[0033]
In this variation, in the rolling bearing 6 on the pinion gear side in which the deep groove ball bearing 61 and the thrust ball bearing 62 are arranged side by side, the width dimensions of the race rings 66 and 67 of the thrust ball bearing 62 are reduced, and the deep groove ball bearing 61 It is characterized by being press-fitted between the outer ring 64 and the pinion gear 3.
[0034]
The other configuration is the same as the example shown in FIGS.
(Embodiment 2)
A second embodiment of the present invention will be described with reference to FIG.
[0035]
FIG. 4 shows a partial cross-sectional view of the pinion shaft supporting bearing device in the second embodiment.
[0036]
In the second embodiment, the rolling bearing 5 on the companion flange side is an angular ball bearing, the rolling bearing 6 on the pinion gear side is the deep groove ball bearing 61 and the thrust needle roller bearing 71, and the thrust needle roller bearing 71 is the deep groove ball. It is characterized by being arranged side by side so as to be closer to the pinion gear than the bearing 61. Other configurations are the same as those in the first embodiment.
[0037]
That is, the deep groove ball bearing 61 of the rolling bearing 5 on the companion flange side and the rolling bearing 6 on the pinion gear side is configured in the same manner as in the first embodiment. The thrust needle roller bearing 71 includes a pair of race rings 72 and 73 and a needle roller group 74 held by a cage 75.
[0038]
One bearing ring 72 of the thrust needle roller bearing 71 is pressed against the back surface of the pinion gear 3 and is press-fitted into the pinion shaft 4, and the other bearing ring 73 is interposed between the pinion shaft 4 and the annular wall 14 via a gap. It is press-fitted into.
[0039]
Further, the inner ring 63 of the deep groove ball bearing 61 is press-fitted into the pinion shaft 4 through a gap between the inner ring 63 and the raceway ring 73 of the thrust needle roller bearing 71, and the outer ring 64 is pressed against the raceway ring 73 to the annular wall 14. Press fit.
[0040]
The rolling bearing 6 press-fits the raceway ring 72 of the thrust needle roller bearing 71 and the inner ring 63 of the deep groove ball bearing 61 into the pinion shaft 4 in a state where the deep groove ball bearing 61 and the thrust needle roller bearing 71 are arranged side by side. The outer ring 64 of the deep groove ball bearing 61 and the raceway ring 73 of the thrust needle roller bearing 71 are press-fitted into the annular wall 14 by being incorporated from the large-diameter side opening of the bearing case 1a.
[0041]
The rolling bearing 5 presses the inner ring 51 into the pinion shaft 4 and presses the outer ring 52 into the annular wall 13.
[0042]
Further, the companion flange 7 is spline-fitted to the small diameter portion 44 on the drive shaft side of the pinion shaft 4, and the nut 15 serving as a fastening means is fastened to the companion flange 7. As a result, the rolling bearings 5 and 6 are sandwiched between the pinion gear 3 and the companion flange 7 and fixed to the bearing case portion 1a.
[0043]
In this way, the deep groove ball bearing 61 receives a radial load, the thrust needle roller bearing 71 receives an axial load, and the rolling bearing 5 receives a radial load and an axial load, thereby causing the pinion shaft 4 to move. The differential case 1 is rotatably supported.
[0044]
In the pinion shaft support bearing device configured as described above, the same effect as in the first embodiment can be obtained.
[0045]
In the rolling bearing 6 on the pinion gear side, the deep groove ball bearing 61 may be provided on the pinion gear 3 side from the thrust bearings 62 and 71.
[0046]
The thrust ball bearing 62 and the thrust needle roller bearing 71 are examples of a thrust bearing, and are not limited thereto, and various thrust bearings such as a thrust cylindrical roller bearing can be used.
[0047]
Furthermore, in each embodiment, the rolling bearing 5 on the companion flange side is an angular ball bearing, but is not limited to this, for example, the tapered roller bearing shown in FIG. 5 and various radial bearings. And a combination of thrust bearings.
[0048]
【The invention's effect】
According to the pinion shaft support bearing device of the present invention, it is possible to obtain an effect that the rotational torque is reduced and the efficiency of the differential device is improved.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a differential device to which a pinion shaft support bearing device according to a first embodiment of the present invention is applied.
FIG. 2 is a partial cross-sectional view of the pinion shaft support bearing device according to the first embodiment of the present invention.
FIG. 3 is a partial cross-sectional view of a modification of the pinion shaft support bearing device according to the first embodiment of the present invention.
FIG. 4 is a partial cross-sectional view of a pinion shaft support bearing device according to a second embodiment of the present invention.
FIG. 5 is a cross-sectional view of a differential device in a conventional example.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Differential case 2 Differential transmission mechanism 2a Ring gear 3 Pinion gear 4 Pinion shaft 5 Rolling bearing on the companion flange side 6 Rolling bearing on the pinion gear side 7 Companion flange 15 Nut (fastening means)
61 Deep groove ball bearing 62 Thrust ball bearing 71 Thrust needle roller bearing

Claims (2)

ピニオン軸の一端に設けたピニオンギヤと、他端に設けたコンパニオンフランジとの間に、前記ピニオン軸をディファレンシャルケースに対して回転自在に支持する軸心方向に並設した一対の転がり軸受を装着してなるピニオン軸支持用軸受装置であって、
ピニオンギヤ側の転がり軸受は、深溝玉軸受とスラスト軸受を軸心方向に並設し、かつ、前記スラスト軸受を前記深溝玉軸受よりピニオンギヤ側に配置してなり、
前記スラスト軸受は一対の軌道輪の間に転動体を介装してなり、一方の軌道輪が前記ピニオンギヤの背面に圧接されて前記ピニオン軸に圧入固定され、他方の軌道輪が前記ピニオン軸との間に隙間を介して前記ディファレンシャルケースの軸受ケース部に圧入固定され、
前記深溝玉軸受は内輪と外輪の間に玉を介装してなり、前記内輪が前記スラスト軸受の他方の軌道輪との間に隙間を介して前記ピニオン軸に圧入固定され、前記外輪が前記スラスト軸受の他方の軌道輪に圧接されて前記ディファレンシャルケースの軸受ケース部に圧入固定され、
前記コンパニオンフランジを締結手段にて前記ピニオンギヤ方向に締結することにより前記一対の転がり軸受を前記ディファレンシャルケースの軸受ケース部に固定したことを特徴とするピニオン軸支持用軸受装置。Between a pinion gear provided at one end of the pinion shaft and a companion flange provided at the other end, a pair of rolling bearings arranged in parallel in the axial direction for rotatably supporting the pinion shaft with respect to the differential case is mounted. A pinion shaft support bearing device comprising:
The pinion gear side rolling bearing comprises a deep groove ball bearing and a thrust bearing arranged side by side in the axial direction, and the thrust bearing is arranged closer to the pinion gear than the deep groove ball bearing,
The thrust bearing has a rolling element interposed between a pair of race rings, one race ring is pressed against the back surface of the pinion gear and press-fitted and fixed to the pinion shaft, and the other race ring is connected to the pinion shaft. Is press-fitted and fixed to the bearing case portion of the differential case through a gap between
The deep groove ball bearing has a ball interposed between an inner ring and an outer ring, the inner ring is press-fitted and fixed to the pinion shaft through a gap between the other bearing ring of the thrust bearing, and the outer ring is Pressed against the other bearing ring of the thrust bearing and press-fitted into the bearing case portion of the differential case,
A pinion shaft support bearing device, wherein the pair of rolling bearings are fixed to a bearing case portion of the differential case by fastening the companion flange in the pinion gear direction by fastening means. ピニオンギヤ側の転がり軸受のスラスト軸受が、スラスト針状ころ軸受またはスラスト玉軸受からなることを特徴とする請求項１記載のピニオン軸支持用軸受装置。  2. The pinion shaft support bearing device according to claim 1, wherein the thrust bearing of the pinion gear side rolling bearing is a thrust needle roller bearing or a thrust ball bearing.
JP2001366070A 2001-11-30 2001-11-30 Bearing device for pinion shaft support Expired - Fee Related JP4069616B2 (en)

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DE102004055422A1 (en) * 2004-11-17 2006-05-24 Schaeffler Kg Construction unit with load dependent osculation e.g. for antifriction bearing, has tracks defining construction unit and defining component and bearings which shift between construction units on tracks
DE102005058396B3 (en) * 2005-12-07 2007-02-08 Ab Skf Bearing unit for bearing shaft part has outer bearing ring in boring in housing, including running tracks for both radial bearings and both axial bearings
DE102013208208A1 (en) * 2013-05-06 2014-11-06 Aktiebolaget Skf Bearing arrangement, bearing and bevel pinion shaft
CN111288146B (en) * 2020-02-14 2021-07-20 株洲齿轮有限责任公司 Transmission and automobile
CN115163751A (en) * 2022-06-27 2022-10-11 中国第一汽车股份有限公司 Electric automobile decelerator and electric automobile

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CN105782238A (en) * 2016-04-21 2016-07-20 浙江天马轴承有限公司 Radial and axial composite cylindrical roller bearing

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