JP3757309B2 - Pinion shaft support bearing unit - Google Patents

Pinion shaft support bearing unit Download PDF

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Publication number
JP3757309B2
JP3757309B2 JP2000155813A JP2000155813A JP3757309B2 JP 3757309 B2 JP3757309 B2 JP 3757309B2 JP 2000155813 A JP2000155813 A JP 2000155813A JP 2000155813 A JP2000155813 A JP 2000155813A JP 3757309 B2 JP3757309 B2 JP 3757309B2
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Japan
Prior art keywords
pinion shaft
raceway surface
inner ring
bearing unit
pinion
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Expired - Fee Related
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JP2000155813A
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Japanese (ja)
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JP2001336603A (en
Inventor
邦彦 横田
正典 曽和
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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
    • F16C19/22—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
    • F16C19/38—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 two or more rows of rollers
    • F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a pinion shaft supporting bearing unit capable of restraining irregularity of a preload and irregularity of the pinion height after incorporation in the pinion shaft supporting bearing unit by outwardly combining double row conical roller bearings having high load capacity. SOLUTION: An inner race raceway surface 12a of a head side (small gear 11 forming side) conical roller bearing of a pinion shaft 1 is integrally formed on the pinion shaft 1, a small collar corresponding to the inner race raceway surface 12a is not formed, the small end side moving end of the raceway surface 12a of a conical roller 3 and a cage 3a incorporated into the raceway surface 12a is regulated by the other conical roller bearing inner race 2 composed of a separate member, the irregularity of the preload and the irregularity of the pinion height by integration of the raceway surface 12a are restrained, and a calking process of the cage 3a incorporated into the inner race raceway surface 12a is obviated so that the pinion shaft supporting bearing unit can be easily assembled.

Description

【０００１】
【発明の属する技術分野】
本発明は、自動車のデファレンシャルギアのピニオン軸を回転自在に支持するピニオン軸支持用軸受ユニットに関する。
【０００２】
【従来の技術】
自動車のデファレンシャルギアのピニオン軸は、一般に、一端に歯車が一体形成され、他端にはプロペラシャフトに対して連結するための接続フランジが固定され、ハウジングに対して軸受ユニットを介して回転自在に支持される。
【０００３】
このようなピニオン軸を支持するための軸受ユニットは、通常、ピニオン軸の軸方向に所定の距離を開けて２つの転がり軸受を配した構造を採る。ピニオン軸には比較的大きなラジアル荷重並びにスラスト荷重が作用するため、これらの各方向への定格荷重の大きな円すいころ軸受を外向き（小鍔どうしが突き合わされた状態）に組み合わせた構造とすることが、寿命を含めて総合的に最も好ましい構造と言える。
【０００４】
図３に２つの円すいころ軸受を外向きに組み合わせた従来のピニオン軸支持用の軸受ユニットの構成例を断面図で示す。この例においては、ピニオン軸４１に２つの内輪４２ａ，４２ｂを外向きに圧入するとともに、２つの軌道面が形成された複列の外輪４３をハウジング４４に固定している。ピニオン軸４１の一端には小歯車（ピニオンヘッド）４１１が一体形成されており、また、他端には雄ねじ４１２が刻設されている。そして、この他端側から、プロペラシャフトに対して連結するための接続フランジ４５が挿入された状態で、雄ねじ４１２にナット４６をねじ込むことによって、ピニオン軸４１に対して接続フランジ４５が固定される。なお、４７は、組立時において内輪４２ａ，４２ｂが相互に分離してしまうことを防止するための分離防止リングである。
【０００５】
【発明が解決しようとする課題】
ところで、以上のように複列の円すいころ軸受を用いたピニオン軸支持用軸受ユニットにおいては、以下に示すような問題がある。
【０００６】
すなわち、ピニオンヘッド側の内輪４２ａと軸の嵌め合いがばらつくと、組込後の予圧のばらつきが大きくなるとともに、図４においてＨで示されるピニオンハイトのばらつきが大となってしまうという問題がある。
【０００７】
本発明の目的は、負荷能力の高い複列の円すいころ軸受を外向きに組み合わせたピニオン軸支持用軸受ユニットの組込後の予圧のばらつきを抑制し、かつ、ピニオンハイトのばらつきを抑えることにある。
【０００８】
【課題を解決するための手段】
上記した目的を達成するため、本発明のピニオン軸支持用軸受ユニットは、デファレンシャルギアのピニオン軸を支持するための軸受ユニットで、複列の円すいころ軸受軌道面が形成されてハウジングに対して固定される外輪と、その外輪の各軌道面に対応するようにピニオン軸に対して固定配置された２つの内輪軌道面との間に、それぞれ複数の円すいころが転動自在に配置されてなるピニオン軸支持用軸受ユニットにおいて、上記２つの内輪軌道面のうち、ヘッド側の内輪軌道面が上記ピニオン軸の外周面に一体形成され、かつ、他方の内輪軌道面は別部材からなる内輪に形成されてピニオン軸に圧入固定されているとともに、上記ピニオン軸に一体に形成された内輪軌道面の小端側には小鍔が形成されておらず、当該内輪軌道面に転動自在に配置される複数の円すいころは、上記別部材からなる内輪の端部によりその移動が規制されるように構成されていることによって特徴づけられる。
【０００９】
本発明は、ピニオン軸のヘッド側（ギア形成側）の内輪軌道面をピニオン軸の表面に直接的に形成することにより所期の目的を達成しようとするものである。
【００１０】
すなわち、ピニオン軸の表面にヘッド側の内輪軌道面を直接形成することにより、内輪とピニオン軸の嵌め合いのばらつきに起因する予圧のばらつき並びにピニオンハイトのばらつきが解消される。
【００１１】
ここで、ヘッド側の内輪軌道面をピニオン軸の表面に形成した場合には、保持器と円すいころのセットをピニオン軸のヘッド側と反対側の端部から挿入する必要があるが、保持器として通常の円すいころ軸受に多用されているプレス保持器を用いる場合、ヘッド側の軌道面用に小鍔を形成すると、保持器と円すいころからなるセットがその小鍔を越えて軌道面にまで達するためには、保持器を一旦開いた後に閉じる、いわゆる保持器のカシメ工程が必要となる。この保持器のカシメは、ピニオン軸のヘッド側と反対側から行う必要があり、極めて特殊な治具等を用いなければ行うことができず、極めて困難な作業となる。
【００１２】
そこで、本発明においては、ピニオン軸のヘッド側に設けた内輪用軌道面に対しては小鍔を設けず、従って保持器と円すいころのセットは、保持器を開くことなくそのままピニオン軸のヘッド側と反対側から挿入して内輪軌道面にまで至らせることができる。そして、この発明においては、この内輪用軌道面に小鍔を設けないことから、この軌道面に配置される保持器と円すいころのセットが内輪軌道面の小端側に移動して各円すいころが分離してしまうことになるが、その移動端を、別部材からなるもう一方の内輪の端部によって規制することで、問題は生じない。
【００１３】
【発明の実施の形態】
以下、図面を参照しつつ本発明の好適な実施の形態について説明する。
図１は本発明の実施の形態の構成を示す軸平行断面図である。
【００１４】
ピニオン軸１の一端には小歯車１１が一体形成されており、その小歯車１１に隣接して、円すいころ軸受内輪用の大鍔１２ｂと軌道面１２ａとが一体形成されている。この軌道面１２ａの小端側には小鍔は形成されておらず、ぬすみ部１２ｃを介して円筒面１２ｄが一体形成され、その円筒面１２ｄの外径寸法は軌道面１２ａの小端径と同等となっている。この軌道面１２ａの外側には、複数の円すいころ３が保持器３ａによって周方向に一定のピッチで保持された状態で配置されている。
【００１５】
上記の円筒面１２ｄの形成位置に隣接して、ピニオン軸１に対して別部材からなる円すいころ軸受の内輪２が、複数の円すいころ４並びにその各円すいころ４を周方向に一定のピッチで保持する保持器４ａが組み込まれた状態で圧入されている。この内輪２は、その小端側が前記した軌道面１２ａの小端側に対向する向きに圧入されている。また、この内輪２は、通常のものと同様に軌道面２ａ，大鍔２ｂおよび小鍔２ｃが形成されているとともに、その小鍔２ｃには軸方向に延出する延出部２ｄが一体的に形成されている。そして、この延出部２ｄが、軌道面１２ａの小端側に形成されている円筒面１２ｄの表面の一部を覆い、当該軌道面１２ａのための小鍔の役割を担っている。すなわち、軌道面１２ａに対して組み込まれた複数の円すいころ３および保持器３ａの組立体の当該軌道面１２ａの小端側への移動端は、隣接して圧入される内輪２の小鍔２ｃに一体形成された延出部２ｄによって規制されるようになっている。
【００１６】
ピニオン軸１の外側には、軌道面１２ａ上の各円すいころ３と、軌道面２ａ上の各円すいころ４のための外輪軌道面５ａ，５ｂが一体的に形成された複列の外輪５が設けられており、この外輪５はハウジング６に対してハイト調整シム６ａを介して固定されている。また、外輪５と内輪２の間には、これらの間に形成されるリング状空間を密封するための密封シール７が配置されている。なお、８はスリンガである。
【００１７】
ピニオン軸１の他端側には、プロペラシャフトに連結するための接続フランジ９が固定されている。この接続フランジ９の内面には、ピニオン軸１の他端側の表面に形成されているセレーション溝と噛み合うセレーション溝が形成されて回り止めが施された状態で、カシメによってピニオン軸１に固定されている。すなわち、ピニオン軸１の他端面には孔１３が形成されて筒状を呈しているとともに、その筒状部分は焼き戻しもしくは防炭が施されて硬度が低くされている。そして、その筒状部分が接続フランジ９に形成された貫通孔９ａ内に挿入された状態で、外側に塑性変形されることによって接続フランジ９が固定されている。
【００１８】
以上の実施の形態において特に注目すべき点は、複列の円すいころ軸受を構成する一方の内輪軌道面１２ａおよび大鍔１２ｂがピニオン軸１に一体形成され、また、この内輪軌道面１２ａには小鍔が付設されておらずに円筒面１２ｄとなっているとともに、その小鍔の役割を他方の内輪軌道面２ａが形成された別部材からなる内輪２に形成されている延出部２ｄが担っている点である。
【００１９】
これにより、複数の円すいころ３を保持して内輪軌道面１２ａに対して組み付けられる保持器３ａは、内輪軌道面１２ａの小端径と同等の外径を有する円筒面１２ｄを通過するだけでいいため、組付けに際して開いた後に閉じる、いわゆるカシメ工程が不要となり、単に内輪軌道面１２ａの外側に挿入するだけでよくなる。また、円すいころ３および保持器３ａを内輪軌道面１２ａの外側に挿入した後、円すいころ４および保持器４ａが既にセットされた内輪２をピニオン軸１に圧入してその延出部２ｄを円筒面１２ｄ上に位置させることで、内輪軌道面１２ａ上の円すいころ３および保持器３ａが脱落してしまうことがない。そして、内輪軌道面１２ａおよび大鍔１２ｂをピニオン軸１に一体形成しているが故に、これらを別部材の内輪に形成してピニオン軸１に圧入する場合に比して、その内輪とピニオン軸１との嵌め合いのばらつきに起因して生じる可能性のある組込後の予圧のばらつき、ピニオンハイトのばらつきが生じることがない。また、内輪軌道面１２ａをピニオン軸１に一体形成することにより、ピニオン軸１自体の曲げ剛性が向上するとともに、大鍔１２ｂの強度も向上する。
【００２０】
また、以上の実施の形態によると、ピニオン軸１に設けたセンター孔を基準としてヘッド側（小歯車１１側）の内輪軌道面の加工が行えることから、回転精度が向上するという利点もある。
【００２１】
また、以上の実施の形態において更に注目すべき点は、接続フランジ９がピニオン軸１に対してカシメによって固定されている点であり、従来のナットの締結による固定に比して、その組立工数を削減することができると当時に、全体としての重量を軽減することができる。
【００２２】
図２に本発明の他の実施の形態の軸平行断面図を示す。この例においては、一方の内輪軌道面１２ａおよび大鍔１２ｂがピニオン軸１に一体形成され、た方の内輪軌道面２ａおよび大鍔２ｂ，小鍔２ｃは別部材の内輪２に形成されてピニオン軸１に圧入され、かつ、その小鍔２ｃから延出した延出部２ｄが内輪軌道面１２ａ用の小鍔の役割を担っている点において先の例と同じであるが、接続フランジ９はピニオン軸１を塑性変形させるカシメによらず、図３に示した従来のものと同様に、ピニオン軸１に形成された雄ねじ１４にナット１５を締結することによって当該ピニオン軸１に固定されている。
【００２３】
この図２の実施の形態によっても、先の例と同様に組込後の予圧のばらつきおよびピニオンハイトのばらつきが生じることがなく、内輪軌道面１２ａをピニオン軸１に一体形成することによるピニオン軸１自体の曲げ剛性の向上、並びに大鍔１２ｂの強度向上を奏することができる。
【００２４】
【発明の効果】
以上のように、本発明によれば、ピニオン軸を支承する２つの円すいころ軸受のうち、小歯車側の軸受の内輪をピニオン軸に対して一体形成するとともに、その内輪の賞嘆側には小鍔を形成せず、その内輪に対して組み込まれる円すいころと保持器の小鍔側への移動端を、別部材からなりピニオン軸に圧入された他方の内輪の小鍔側の端部により規制するように構成しているので、小歯車側（ヘッド側）の内輪とピニオン軸とのはめあいのばらつきに起因する組込後の予圧のばらつき並びにピニオンハイトのばらつきが生じず、ピニオン軸の曲げ剛性および当該ヘッド側の軸受の大鍔の強度の向上をも達成することができるとともに、ピニオン軸のセンター孔を基準としてヘッド側の内輪軌道面の加工を行えることから、回転精度を向上させることができる。しかも、その一体形成した内輪に組み込まれる保持器をプレス保持器としてもそのカシメ工程が不要となり、容易に組み込むことができる。
【図面の簡単な説明】
【図１】 本発明の実施の形態の構成を示す軸平行断面図である。
【図２】 本発明の他の実施の形態の軸平行断面図である。
【図３】 複列円すいころ軸受を用いた従来のピニオン軸支持用軸受ユニットの構成例を示す軸平行断面図である。
【符号の説明】
１ ピニオン軸
１１ 小歯車
１２ａ 内輪軌道面
１２ｂ 大鍔
１２ｃ ぬすみ部
１２ｄ 円筒面
１３ 孔
１４ 雄ねじ
１５ ナット
２ 内輪
２ａ 軌道面
２ｂ 大鍔
２ｃ 小鍔
２ｄ 延出部
３，４ 円すいころ
５ 外輪
５ａ，５ｂ 軌道面
６ ハウジング
９ 接続フランジ[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pinion shaft support bearing unit that rotatably supports a pinion shaft of a differential gear of an automobile.
[0002]
[Prior art]
In general, a pinion shaft of an automobile differential gear is integrally formed with a gear at one end, and a connection flange for coupling to a propeller shaft is fixed at the other end, and is rotatable with respect to a housing via a bearing unit. Supported.
[0003]
Such a bearing unit for supporting the pinion shaft usually has a structure in which two rolling bearings are arranged at a predetermined distance in the axial direction of the pinion shaft. Since a relatively large radial load and thrust load act on the pinion shaft, a tapered roller bearing with a large rated load in each of these directions should be combined outward (with the small flanges butted together). However, it can be said that the most preferable structure comprehensively including the lifetime.
[0004]
FIG. 3 is a cross-sectional view showing a configuration example of a conventional pinion shaft supporting bearing unit in which two tapered roller bearings are combined outwardly. In this example, two inner rings 42 a and 42 b are press-fitted outwardly to a pinion shaft 41, and a double row outer ring 43 formed with two raceway surfaces is fixed to a housing 44. A small gear (pinion head) 411 is integrally formed at one end of the pinion shaft 41, and a male screw 412 is engraved at the other end. Then, the connection flange 45 is fixed to the pinion shaft 41 by screwing the nut 46 into the male screw 412 with the connection flange 45 to be connected to the propeller shaft inserted from the other end side. . Reference numeral 47 denotes a separation preventing ring for preventing the inner rings 42a and 42b from separating from each other during assembly.
[0005]
[Problems to be solved by the invention]
Incidentally, the pinion shaft support bearing unit using the double row tapered roller bearing as described above has the following problems.
[0006]
That is, when the fitting between the inner ring 42a on the pinion head side and the shaft varies, there is a problem that the variation in preload after incorporation becomes large and the variation in pinion height indicated by H in FIG. 4 becomes large. .
[0007]
An object of the present invention is to suppress variations in preload after incorporation of a pinion shaft support bearing unit in which double-row tapered roller bearings having a high load capacity are combined outward, and to suppress variations in pinion height. is there.
[0008]
[Means for Solving the Problems]
In order to achieve the above object, the pinion shaft support bearing unit of the present invention is a bearing unit for supporting the pinion shaft of a differential gear, and a double row tapered roller bearing raceway surface is formed and fixed to the housing. A pinion in which a plurality of tapered rollers are arranged so as to roll between an outer ring to be rotated and two inner ring raceway surfaces fixed to the pinion shaft so as to correspond to each raceway surface of the outer ring. In the shaft support bearing unit, of the two inner ring raceway surfaces, the head-side inner ring raceway surface is integrally formed on the outer peripheral surface of the pinion shaft, and the other inner ring raceway surface is formed on an inner ring made of a separate member. The pinion shaft is press-fitted and fixed, and the small end side of the inner ring raceway surface formed integrally with the pinion shaft is not formed with a small edge, and the inner ring raceway surface is rolled. A plurality of tapered rollers arranged stationary is characterized by its movement is arranged to be regulated by the end of either Ranaru inner ring the separate member.
[0009]
The present invention seeks to achieve the intended purpose by directly forming the inner ring raceway surface on the head side (gear forming side) of the pinion shaft on the surface of the pinion shaft.
[0010]
That is, by directly forming the head-side inner ring raceway surface on the surface of the pinion shaft, the variation in preload and the variation in pinion height due to the variation in the fitting between the inner ring and the pinion shaft are eliminated.
[0011]
Here, when the inner ring raceway surface on the head side is formed on the surface of the pinion shaft, it is necessary to insert a set of a cage and a tapered roller from the end of the pinion shaft opposite to the head side. When using a press cage that is often used for ordinary tapered roller bearings, if a small cage is formed for the raceway surface on the head side, the set consisting of the cage and the tapered roller extends beyond the minor cage to the raceway surface. In order to achieve this, a so-called caulking process of the cage, in which the cage is once opened and then closed, is required. Caulking of the cage needs to be performed from the side opposite to the head side of the pinion shaft, and cannot be performed unless a very special jig or the like is used, which is an extremely difficult operation.
[0012]
Therefore, in the present invention, no small bristle is provided for the inner ring raceway surface provided on the head side of the pinion shaft, and therefore the set of the cage and the tapered roller is directly disposed on the pinion shaft head without opening the cage. It can be inserted from the opposite side to the inner ring raceway surface. In the present invention, since no gavel is provided on the raceway surface for the inner ring, a set of a cage and a tapered roller arranged on the raceway surface moves to the small end side of the inner ring raceway surface, and each tapered roller However, there is no problem by restricting the moving end by the end of the other inner ring made of another member.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is an axial parallel sectional view showing the configuration of the embodiment of the present invention.
[0014]
A small gear 11 is integrally formed at one end of the pinion shaft 1, and a large flange 12 b for a tapered roller bearing inner ring and a raceway surface 12 a are integrally formed adjacent to the small gear 11. A small edge is not formed on the small end side of the raceway surface 12a, and a cylindrical surface 12d is integrally formed via a shank portion 12c. The outer diameter of the cylindrical surface 12d is equal to the small end diameter of the raceway surface 12a. It is equivalent. This is outside of the raceway surface 12a, they are arranged in a state in which a plurality of circular tapered roller 3 is held at a constant pitch in the circumferential direction by a cage 3a.
[0015]
Adjacent to the position where the cylindrical surface 12d is formed, the inner ring 2 of the tapered roller bearing, which is a separate member with respect to the pinion shaft 1, has a plurality of tapered rollers 4 and each tapered roller 4 at a constant pitch in the circumferential direction. The retainer 4a to be held is press-fitted in a state where it is incorporated. The inner ring 2 is press-fitted so that the small end side thereof faces the small end side of the raceway surface 12a. Further, the inner ring 2 is formed with a raceway surface 2a, a large collar 2b and a small collar 2c in the same manner as a normal one, and an extending portion 2d extending in the axial direction is integrally formed with the small collar 2c. Is formed. The extending portion 2d covers a part of the surface of the cylindrical surface 12d formed on the small end side of the raceway surface 12a, and plays a role of a gavel for the raceway surface 12a. That is, the moving end to the small end side of the raceway surface 12a of the assembly of the plurality of tapered rollers 3 and the cage 3a incorporated in the raceway surface 12a is adjacent to the small ring 2c of the inner ring 2 to be press-fitted. It is regulated by an extending portion 2d formed integrally with the.
[0016]
On the outside of the pinion shaft 1, there are double-row outer rings 5 formed integrally with each tapered roller 3 on the raceway surface 12a and outer ring raceway surfaces 5a and 5b for each tapered roller 4 on the raceway surface 2a. The outer ring 5 is fixed to the housing 6 via a height adjusting shim 6a. Further, between the outer ring 5 and the inner ring 2, a sealing seal 7 for sealing a ring-shaped space formed therebetween is arranged. In addition, 8 is a slinger.
[0017]
A connection flange 9 for coupling to the propeller shaft is fixed to the other end side of the pinion shaft 1. A serration groove that meshes with a serration groove formed on the surface of the other end of the pinion shaft 1 is formed on the inner surface of the connection flange 9 and is fixed to the pinion shaft 1 by caulking. ing. That is, a hole 13 is formed on the other end surface of the pinion shaft 1 to form a cylinder, and the cylindrical portion is tempered or carburized to reduce its hardness. The connecting flange 9 is fixed by being plastically deformed outward while the cylindrical portion is inserted into a through hole 9 a formed in the connecting flange 9.
[0018]
Of particular note in the above embodiment is that one inner ring raceway surface 12a and a large collar 12b constituting a double row tapered roller bearing are formed integrally with the pinion shaft 1, and the inner ring raceway surface 12a includes An extension portion 2d formed on the inner ring 2 made of another member on which the other inner ring raceway surface 2a is formed has a cylindrical surface 12d with no gavel attached thereto and the role of the gavel. It is the point that bears.
[0019]
Thus, the cage 3a that holds the plurality of tapered rollers 3 and is assembled to the inner ring raceway surface 12a only needs to pass through the cylindrical surface 12d having an outer diameter equivalent to the small end diameter of the inner ring raceway surface 12a. This eliminates the need for a so-called caulking process that opens and closes after assembling, and only requires insertion outside the inner raceway surface 12a. Further, after the tapered roller 3 and the cage 3a are inserted outside the inner ring raceway surface 12a, the inner ring 2 on which the tapered roller 4 and the cage 4a have already been set is press-fitted into the pinion shaft 1, and the extending portion 2d is cylindrical. By positioning on the surface 12d, the tapered roller 3 and the cage 3a on the inner ring raceway surface 12a are not dropped off. And since the inner ring raceway surface 12a and the large collar 12b are integrally formed with the pinion shaft 1, the inner ring and the pinion shaft are compared with the case where these are formed in the inner ring as another member and press-fitted into the pinion shaft 1. No variation in preload or variation in pinion height that may occur due to variation in fitting with No. 1 occurs. Further, by forming the inner ring raceway surface 12a integrally with the pinion shaft 1, the bending rigidity of the pinion shaft 1 itself is improved and the strength of the large collar 12b is also improved.
[0020]
Moreover, according to the above embodiment, since the inner ring raceway surface on the head side (the small gear 11 side) can be processed on the basis of the center hole provided in the pinion shaft 1, there is an advantage that the rotation accuracy is improved.
[0021]
Further, in the above embodiment, the point to be further noted is that the connection flange 9 is fixed to the pinion shaft 1 by caulking, and the number of assembling steps is larger than the conventional fixing by fastening the nut. And can reduce the overall weight at that time.
[0022]
FIG. 2 shows an axial parallel sectional view of another embodiment of the present invention . In this example, one inner ring raceway surface 12a and the large collar 12b are integrally formed with the pinion shaft 1, and the other inner ring raceway surface 2a, the large collar 2b, and the small collar 2c are formed on the inner ring 2 which is a separate member. The connecting flange 9 is the same as the previous example in that the extending portion 2d that is press-fitted into the shaft 1 and extends from the gavel 2c plays the role of a gavel for the inner ring raceway surface 12a. irrespective of the pinion shaft 1 to the caulking to plastically deform, similar to that of prior art shown in FIG. 3, and is fixed to the pinion shaft 1 by fastening the nut 15 to the male screw 14 formed on the pinion shaft 1 .
[0023]
This also affects the embodiment of FIG. 2, without variation of the preload variations and pinion height of the after integration as in the previous example occurs, pinion due to the integrally formed inner ring raceway surface 12a on the pinion shaft 1 The bending rigidity of the shaft 1 itself can be improved, and the strength of the large collar 12b can be improved .
[0024]
【The invention's effect】
As described above, according to the present invention, of the two tapered roller bearings for supporting the pinion shaft, the inner ring of the small gear side bearing is integrally formed with the pinion shaft, The tapered roller incorporated into the inner ring without forming a gavel and the moving end of the cage toward the gavel side are separated from the edge of the other inner ring press-fitted into the pinion shaft. Because it is configured to regulate, there is no variation in preload and pinion height after assembly due to variation in fit between the inner ring on the small gear side (head side) and the pinion shaft, and pinion shaft bending The rigidity of the bearing on the head side can be improved, and the inner ring raceway surface on the head side can be processed on the basis of the center hole of the pinion shaft. It is possible. Moreover, even if the retainer incorporated in the integrally formed inner ring is used as a press retainer, the caulking process is not required and can be easily incorporated.
[Brief description of the drawings]
FIG. 1 is an axial parallel sectional view showing a configuration of an embodiment of the present invention.
FIG. 2 is an axial parallel cross-sectional view of another embodiment of the present invention.
FIG. 3 is an axial parallel cross-sectional view showing a configuration example of a conventional pinion shaft supporting bearing unit using a double row tapered roller bearing.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Pinion shaft 11 Small gear 12a Inner ring raceway surface 12b Large collar 12c Slack part 12d Cylindrical surface 13 Hole 14 Male screw 15 Nut
2 Inner ring 2a Raceway surface 2b Large flange 2c Small flange 2d Extension part 3, 4 Tapered roller 5 Outer ring 5a, 5b Raceway 6 Housing 9 Connection flange

Claims (1)

デファレンシャルギアのピニオン軸を支持するための軸受ユニットで、複列の円すいころ軸受軌道面が形成されてハウジングに対して固定される外輪と、その外輪の各軌道面に対応するようにピニオン軸に対して固定配置された２つの内輪軌道面との間に、それぞれ複数の円すいころが転動自在に配置されてなるピニオン軸支持用軸受ユニットにおいて、
上記２つの内輪軌道面のうち、ヘッド側の内輪軌道面が上記ピニオン軸の外周面に一体形成され、かつ、他方の内輪軌道面は別部材からなる内輪に形成されてピニオン軸に圧入固定されているとともに、上記ピニオン軸に一体に形成された内輪軌道面の小端側には小鍔が形成されておらず、当該内輪軌道面に転動自在に配置される複数の円すいころは、上記別部材からなる内輪の端部によりその移動が規制されるように構成されていることを特徴とするピニオン軸支持用軸受ユニット。A bearing unit for supporting the pinion shaft of a differential gear. A double row tapered roller bearing raceway surface is formed on the outer ring that is fixed to the housing, and the pinion shaft is adapted to correspond to each raceway surface of the outer ring. In the pinion shaft supporting bearing unit in which a plurality of tapered rollers are arranged so as to be freely rotatable between two inner ring raceway surfaces fixedly arranged with respect to each other,
Of the two inner ring raceway surfaces, the inner ring raceway surface on the head side is formed integrally with the outer peripheral surface of the pinion shaft, and the other inner ring raceway surface is formed as an inner ring made of a separate member and is press-fitted and fixed to the pinion shaft. In addition, a small edge is not formed on the small end side of the inner ring raceway surface formed integrally with the pinion shaft, and a plurality of tapered rollers arranged to roll on the inner ring raceway surface are the pinion shaft supporting bearing unit, characterized in that the movement by another member or Ranaru inner end is configured to be regulated.
JP2000155813A 2000-05-26 2000-05-26 Pinion shaft support bearing unit Expired - Fee Related JP3757309B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2000155813A JP3757309B2 (en) 2000-05-26 2000-05-26 Pinion shaft support bearing unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2000155813A JP3757309B2 (en) 2000-05-26 2000-05-26 Pinion shaft support bearing unit

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DE102013212989B4 (en) * 2013-07-03 2015-10-08 Aktiebolaget Skf engine assembly
US9631671B2 (en) 2013-11-14 2017-04-25 Schaeffler Technologies AG & Co., KG Roller bearing assembly for a pinion in a motor vehicle drive train
DE102017222795A1 (en) * 2017-12-14 2019-06-19 Aktiebolaget Skf bearing arrangement
DE102019202840A1 (en) * 2019-03-01 2020-09-03 Aktiebolaget Skf Rolling surface element of a rolling bearing and method for repairing a rolling surface element
DE102019133155A1 (en) * 2019-12-05 2021-01-07 Schaeffler Technologies AG & Co. KG Multi-row rolling bearing arrangement
DE102019133158A1 (en) * 2019-12-05 2021-06-10 Schaeffler Technologies AG & Co. KG Multi-row rolling bearing arrangement

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