JP3623309B2 - Defpinion tapered roller bearing device - Google Patents

Defpinion tapered roller bearing device Download PDF

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Publication number
JP3623309B2
JP3623309B2 JP10126496A JP10126496A JP3623309B2 JP 3623309 B2 JP3623309 B2 JP 3623309B2 JP 10126496 A JP10126496 A JP 10126496A JP 10126496 A JP10126496 A JP 10126496A JP 3623309 B2 JP3623309 B2 JP 3623309B2
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Prior art keywords
tapered roller
roller bearing
housing
outer ring
axial
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JPH09287617A (en
Inventor
邦彦 横田
博文 百々路
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Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • 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
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • 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)
  • Support Of The Bearing (AREA)
  • General Details Of Gearings (AREA)
  • Rolling Contact Bearings (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明は、デフピニオン（差動小歯車）の円すいころ軸受装置に関する。
【０００２】
【従来の技術】
従来、デフピニオンの円すいころ軸受装置としては、軸とハウジングとの間に軸方向に所定の間隔を隔てて２つの円すいころ軸受を配置したものがある。上記ハウジングは径方向内方に突き出した内周凸部を有し、この内周凸部が上記２つの円すいころ軸受の２つの外輪の間に嵌合して間座の役目を果たしている。また、上記２つの円すいころ軸受の内輪の間には、内輪間座が嵌合されている。従来、軸とハウジングおよび２つの円すいころ軸受は鋼製である。
【０００３】
【発明が解決しようとする課題】
ところで、軽量化の目的で、上記ハウジングを鋼製からアルミ合金製に変えることが検討されている。
【０００４】
しかし、上記ハウジングをアルミ合金製にした場合には、ハウジングの線膨張係数が軸や軸受や内輪間座の線膨張係数よりも大きなことに起因して、使用温度の上下変動により、円すいころ軸受のアキシャル隙間が増減して、予圧不足で円すいころ軸受にガタが発生したり、予圧過大で焼き付いたりするという問題がある。
【０００５】
そこで、この発明の目的は、使用温度の変化による円すいころ軸受の予圧不足や予圧過大を招くことなく、ハウジングをアルミ合金製にして軽量化することができるデフピニオンの円すいころ軸受装置を提供することにある。
【０００６】
【課題を解決するための手段】
上記目的を達成するため、請求項１の発明のデフピニオンの円すいころ軸受装置は、軸と、軸方向に所定の間隔を隔てて上記軸に嵌合されている２つの円すいころ軸受と、一方の円すいころ軸受の内輪と他方の円すいころ軸受の内輪との間に嵌合された内輪間座と、一方の外輪の外周面と他方の外輪の外周面に嵌合されており、かつ、一方の外輪と他方の外輪の間で、一方の外輪の軸方向の端面と他方の外輪の軸方向の端面とに当接する内周凸部を含んだハウジングとを備えたデフピニオンの円すいころ軸受装置において、上記ハウジングがアルミ合金で作製されている一方、上記内輪間座と２つの円すいころ軸受とが鋼で作製されていて、使用温度が上下に変化したときに、上記ハウジングの軸方向寸法の増減に起因する上記円すいころ軸受のアキシャル隙間の減増量を、上記ハウジングの径方向寸法の増減に起因する上記円すいころ軸受のアキシャル隙間の増減量でもって相殺するように、上記ハウジングの内の上記２つの外輪の端面に挟まれた内周凸部の軸方向寸法Ｌ０と、上記円すいころ軸受のころと外輪との接触角θと、外輪とハウジングとの径方向の締め代Ｄとが設定されていることを特徴としている。
【０００７】
したがって、この請求項１の発明によれば、使用温度の変化による円すいころ軸受の予圧不足や予圧過大を招くことなく、ハウジングをアルミ合金製にして軽量化することができる。
【０００８】
また、請求項２の発明は、請求項１に記載のデフピニオンの円すいころ軸受装置において、上記ハウジングの軸方向寸法Ｌ０と上記接触角θと上記締め代Ｄとを、次の（１）式と（２）式と（３）式を満足するような範囲に設定したことを特徴としている。
【０００９】
４０ｍｍ≦Ｌ０≦６０ｍｍ ……… （１）
１８°≦θ≦２５° ……… （２）
３０μｍ≦Ｄ≦８０μｍ ……… （３）
【発明の実施の形態】
以下、この発明を図示の実施の形態により詳細に説明する。
【００１０】
図１に、この発明のデフピニオンの円すいころ軸受装置の実施の形態の要部断面を示す。この円すいころ軸受装置は、軸１とアウター側の円すいころ軸受２とインナー側の円すいころ軸受３と内輪間座５とハウジング６とを有している。
【００１１】
上記ハウジング６はアルミ合金製であり、軸１と円すいころ軸受２および３と内輪間座５は鋼製である。
【００１２】
上記軸１は、小径部７と大径部８とを有している。この小径部７には上記アウター側の円すいころ軸受２が締まり嵌めされている。また、上記大径部８にはインナー側の円すいころ軸受３が締まり嵌めされている。この円すいころ軸受２の内輪１０の小径部１１の軸方向端面１１ａと、上記円すいころ軸受３の内輪１２の小径部１３の軸方向端面１３ａとは対面している。そして、上記軸方向端面１１ａと１３ａに端面５ａと５ｂとが当接するように、内輪間座５が軸１に嵌合されている。
【００１３】
また、円すいころ軸受２の外輪１５は、上記ハウジング６のアウター側の内周面６ａに押圧されており、ハウジング６に対して締まり嵌めされている。また、円すいころ軸受３の外輪１６は、上記ハウジング６のインナー側の内周面６ｂに押圧されており、ハウジング６に対して締まり嵌めされている。そして、上記外輪１５の厚肉部１７の軸方向端面１７ａと上記外輪１６の厚肉部１８の軸方向端面１８ａとは対面している。そして、上記ハウジング６の径方向内方に突き出している円環形状の内周凸部２０が外輪１５と１６との間に嵌合していて、内周凸部２０の軸方向端面２０ａと２０ｂは、外輪１５の軸方向端面１７ａと外輪１６の軸方向端面１８ａに当接している。
【００１４】
上記構成のデフピニオンの円すいころ軸受装置は、ハウジング６がアルミ合金製であるのに対して、軸１と円すいころ軸受２，３と内輪間座５が鋼製であるから、軸１や円すいころ軸受２，３や内輪間座５の線膨張係数よりも、ハウジング６の線膨張係数の方が大きい。具体的には、ハウジング６の線膨張係数は約２０．０〔１０−６／ｄｅｇ〕であり、軸１や軸受２，３の線膨張係数は約１１．２〔１０−６／ｄｅｇ〕である。
【００１５】
したがって、周囲温度が上昇すると、上記ハウジング６のアウター側の内周面６ａは円すいころ軸受２の外輪１５に対して緩み、ハウジング６のインナー側の内周面６ｂは円すいころ軸受３の外輪１６に対して緩む。この緩みは、円すいころ軸受２と３のアキシャル隙間ＡＣ２とＡＣ３を増加させる方向に働く。そして、ころ２１と外輪１５との接触角θ１が小さいほど、上記緩み量に対するアキシャル隙間ＡＣ２の増加量が大きく、ころ２２と外輪１６との接触角θ２が小さいほど、上記緩み量に対するアキシャル隙間ＡＣ３の増加量が大きい。なお、接触角とは、軸方向に対する外輪の軌道面の傾斜角度である。
【００１６】
また、上記周囲温度の上昇によって、上記ハウジング６の内周凸部２０の端面２０ａは円すいころ軸受２の外輪１５の厚肉部１７の軸方向端面１７ａに対して締まり、上記内周凸部２０の端面２０ｂは円すいころ軸受３の外輪１６の厚肉部１８の軸方向端面１８ａに対して締まる。この締まりは、円すいころ軸受２と３のアキシャル隙間ＡＣ２とＡＣ３を減少させる方向に働く。
【００１７】
また、周囲温度が下降したときには、上述とは逆に、ハウジング６の外輪１５，１６に対する径方向の締まりに起因してアキシャル隙間ＡＣ２，ＡＣ３が減少し、ハウジング６の内周凸部２０の外輪１５，１６に対する軸方向の緩みに起因してアキシャル隙間ＡＣ２，ＡＣ３が増加する。
【００１８】
このように、周囲温度が変化したときに、アキシャル隙間ＡＣ２とＡＣ３とを増加させる要因と、減少させる要因とがあるから、この増加量と減少量とを拮抗させるように、上記増加要因と減少要因とを設定することによって、温度変化した時にアキシャル隙間ＡＣ２とＡＣ３が変化しないようにすることができる。
【００１９】
具体的には、上記要因としては、上記２つの外輪１５と１６に挟まれた内周凸部２０の軸方向の寸法Ｌ０と、外輪１５とハウジング６との径方向の締め代Ｄ１と、外輪１６とハウジング６との径方向の締め代Ｄ２、さらには、上記接触角θ１，θ２がある。上記内周凸部２０の軸方向の寸法Ｌ０が大きいほど、周囲温度の増加に対するアキシャル隙間ＡＣ２およびＡＣ３の増加量が大きくなる。また、上記締め代Ｄ１が大きいほど、周囲温度の増加に対するアキシャル隙間ＡＣ２の減少量が大きくなる。また、締め代Ｄ２が大きいほど、周囲温度の増加に対するアキシャル隙間ＡＣ３の減少量が大きくなる。
【００２０】
また、ころ２１と外輪１５との接触角θ１が大きいほど、ハウジング６の径方向への拡大（周囲温度の増加による）に起因するアキシャル隙間ＡＣ２の増加量が小さくなる。また、ころ２２と外輪１６との接触角θ２が大きいほど、ハウジング６の径方向への拡大（周囲温度の増加による）に起因するアキシャル隙間ＡＣ３の増加量が小さくなる。
【００２１】
したがって、たとえば、上記内周凸部２０の軸方向の寸法Ｌ０の増加に起因するＡＣ２とＡＣ３の減少量に、締め代Ｄ１とＤ２の減少に起因するＡＣ２とＡＣ３の増加量が略等しくなるように、上記Ｌ０，Ｄ１，Ｄ２および接触角θ１とθ２を設定することによって、使用温度が変化してもアキシャル隙間ＡＣ２，ＡＣ３が変化することを防止することができる。したがって、使用温度の変化による円すいころ軸受２および３が予圧不足や予圧過大になることを防止できる。したがって、この形態によれば、予圧不足によるガタや予圧過大による焼付を招くことなく、ハウジング６をアルミ合金製にして軽量化することができる。
【００２２】
次に、上記要因としての上記２つの外輪１５と１６に挟まれた内周凸部２０の軸方向の寸法Ｌ０と、外輪１５とハウジング６との径方向の締め代Ｄ１と、外輪１６とハウジング６との径方向の締め代Ｄ２、さらには、上記接触角θ１，θ２の具体的な設定数値を説明する。
【００２３】
この実施の形態では、上記内周凸部２０の軸方向の寸法Ｌ０を５８ｍｍとし、上記締め代Ｄ１を３１μｍ〜８０μｍとし、上記締め代Ｄ２を３１〜８０μｍとした。更には、上記接触角θ１を２０°とし、上記接触角θ２を２０°とした。そして、この実施の形態の円すいころ軸受装置の周囲温度の変化（０℃〜１２０℃）に対するアキシャル隙間ＡＣ２とＡＣ３の変動値を、図２に示す。この図２に示されたような、アキシャル隙間の変動範囲では、予圧不足でガタが発生することがなく、かつ、予圧過大で焼き付くことがない。
【００２４】
尚、上記実施の形態では、凸部２０の軸方向の寸法Ｌ０を５８ｍｍとし、締め代Ｄ１を３１〜８０μｍとし、締め代Ｄ２を３１〜８０μｍとし、接触角θ１を２０°とし、接触角θ２を２０°としたが、凸部２０の軸方向の寸法Ｌ０が次の（１）式を満足しており、締め代Ｄ１，Ｄ２が次の（２）式を満足しており、接触角θ１，θ２が次の（３）式を満足していればよい。このように設定すれば、上述の周囲温度の変化に対するアキシャル隙間ＡＣ２とＡＣ３の変動量を、予圧不足や予圧過大を招かないような値に抑えることができる。上記式（１），（２），（３）の１つでも満足しない場合には、予圧不足や予圧過大になることが実験により分かった。なお、外輪とハウジングとの嵌め合いの隙間減少率Ｋｅは０．２ないし０．３を選んだ。
【００２５】
４０ｍｍ≦Ｌ０≦６０ｍｍ ……… （１）
１８°≦θ≦２５° ……… （２）
３０μｍ ≦Ｄ≦８０μｍ ……… （３）
【発明の効果】
以上より明らかなように、請求項１の発明のデフピニオンの円すいころ軸受装置は、軸と、軸方向に所定の間隔を隔てて上記軸に嵌合されている２つの円すいころ軸受と、一方の円すいころ軸受の内輪と他方の円すいころ軸受の内輪との間に嵌合された内輪間座と、一方の外輪の外周面と他方の外輪の外周面に嵌合されており、かつ、一方の外輪と他方の外輪との間で一方の外輪の軸方向の端面と他方の外輪の軸方向の端面とに当接する内周凸部を含んだハウジングとを備えたデフピニオンの円すいころ軸受装置において、上記ハウジングがアルミ合金で作製されている一方、上記内輪間座と２つの円すいころ軸受とが鋼で作製されていて、使用温度が上下に変化したときに、上記ハウジングの軸方向寸法の増減に起因する上記円すいころ軸受のアキシャル隙間の減増量を、上記ハウジングの径方向寸法の増減に起因する上記円すいころ軸受のアキシャル隙間の増減量でもって相殺するように、上記ハウジングの内の上記２つの外輪の端面に挟まれた内周凸部の軸方向寸法Ｌ０と、上記円すいころ軸受のころと外輪との接触角θと、外輪とハウジングとの径方向の締め代Ｄとが設定されている。
【００２６】
したがって、この請求項１の発明によれば、使用温度の変化による円すいころ軸受の予圧不足や予圧過大を招くことなく、ハウジングをアルミ合金製にして軽量化することができる。
【００２７】
また、請求項２の発明は、請求項１に記載のデフピニオンの円すいころ軸受装置において、上記ハウジングの軸方向寸法Ｌ０と上記接触角θと上記締め代Ｄとを、次の（１）式と（２）式と（３）式を満足するような範囲に設定している。
【００２８】
４０ｍｍ≦Ｌ０≦６０ｍｍ ……… （１）
１８°≦θ≦２５° ……… （２）
３０μｍ ≦Ｄ≦８０μｍ ……… （３）
この請求項２の発明によれば、周囲温度の変化に対する円すいころ軸受のアキシャル隙間の変動量を、予圧不足や予圧過大を招かないような値に抑えることができる。
【図面の簡単な説明】
【図１】この発明のデフピニオンの円すいころ軸受装置の実施の形態の要部断面図である。
【図２】上記実施の形態において、周囲温度の変化に対するアキシャル隙間の変化量を表す特性図である。
【符号の説明】
１…軸、２，３…円すいころ軸受、５…内輪間座、６…ハウジング、
６ａ，６ｂ…内周面、７…小径部、８…大径部、１０，１２…内輪、
１１…小径部、１１ａ…軸方向端面、１３…小径部、
１３ａ…軸方向端面、１５，１６…外輪、１７…厚肉部、
１７ａ…軸方向端面、１８…厚肉部、１８ａ…軸方向端面、
２０…内周凸部、２１，２２…ころ。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a tapered roller bearing device for a differential pinion (differential small gear).
[0002]
[Prior art]
Conventionally, as a tapered roller bearing device of a differential pinion, there is one in which two tapered roller bearings are arranged between a shaft and a housing at a predetermined interval in the axial direction. The housing has an inner circumferential convex portion protruding radially inward, and the inner circumferential convex portion is fitted between the two outer rings of the two tapered roller bearings to serve as a spacer. An inner ring spacer is fitted between the inner rings of the two tapered roller bearings. Conventionally, the shaft and housing and the two tapered roller bearings are made of steel.
[0003]
[Problems to be solved by the invention]
By the way, for the purpose of weight reduction, changing the housing from steel to aluminum alloy has been studied.
[0004]
However, when the housing is made of an aluminum alloy, the linear expansion coefficient of the housing is larger than the linear expansion coefficient of the shaft, the bearing, or the inner ring spacer. There is a problem that the axial gap increases and decreases, and the tapered roller bearing is loose due to insufficient preload or seizes due to excessive preload.
[0005]
SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a differential pinion tapered roller bearing device capable of reducing the weight by making the housing made of an aluminum alloy without causing insufficient preload or excessive preload of the tapered roller bearing due to a change in operating temperature. It is in.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, a tapered roller bearing device of a differential pinion of the invention of claim 1 includes a shaft, two tapered roller bearings fitted to the shaft at a predetermined interval in the axial direction, and one of the tapered roller bearings. An inner ring spacer fitted between the inner ring of the tapered roller bearing and the inner ring of the other tapered roller bearing; fitted to the outer circumferential surface of one outer ring and the outer circumferential surface of the other outer ring; A tapered pinion bearing device for a differential pinion comprising a housing including an inner peripheral convex portion that contacts an axial end surface of one outer ring and an axial end surface of the other outer ring between the outer ring and the other outer ring. Is made of aluminum alloy, while the inner ring spacer and the two tapered roller bearings are made of steel, and when the operating temperature changes up and down, it is caused by the increase or decrease of the axial dimension of the housing The above tapered roller shaft The amount of increase / decrease in the axial clearance is offset by the increase / decrease amount in the axial clearance of the tapered roller bearing caused by the increase / decrease in the radial dimension of the housing. the axial dimension L 0 of the circumferential projection portion in the is characterized in that the contact angle θ between the roller and the outer ring of the tapered roller bearing, the interference D in the radial direction between the outer ring and the housing are set.
[0007]
Therefore, according to the first aspect of the present invention, the housing can be made of an aluminum alloy and can be reduced in weight without causing the preload of the tapered roller bearing to be insufficient or excessively preloaded due to the change in operating temperature.
[0008]
According to a second aspect of the present invention, in the tapered roller bearing device of the differential pinion according to the first aspect, the axial dimension L 0 of the housing, the contact angle θ, and the tightening allowance D are expressed by the following formula (1): And (2) and (3) are set in a range that satisfies the expressions.
[0009]
40 mm ≦ L 0 ≦ 60 mm (1)
18 ° ≦ θ ≦ 25 ° ……… (2)
30 μm ≦ D ≦ 80 μm (3)
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
[0010]
FIG. 1 shows a cross-section of the main part of an embodiment of a tapered roller bearing device of a differential pinion according to the present invention. This tapered roller bearing device includes a shaft 1, an outer tapered roller bearing 2, an inner tapered roller bearing 3, an inner ring spacer 5, and a housing 6.
[0011]
The housing 6 is made of an aluminum alloy, and the shaft 1, the tapered roller bearings 2 and 3, and the inner ring spacer 5 are made of steel.
[0012]
The shaft 1 has a small diameter portion 7 and a large diameter portion 8. The outer tapered roller bearing 2 is tightly fitted to the small diameter portion 7. Further, the inner diameter tapered roller bearing 3 is tightly fitted to the large diameter portion 8. The axial end surface 11a of the small diameter portion 11 of the inner ring 10 of the tapered roller bearing 2 and the axial end surface 13a of the small diameter portion 13 of the inner ring 12 of the tapered roller bearing 3 face each other. The inner ring spacer 5 is fitted to the shaft 1 so that the end faces 5a and 5b abut against the axial end faces 11a and 13a.
[0013]
Further, the outer ring 15 of the tapered roller bearing 2 is pressed against the inner peripheral surface 6 a on the outer side of the housing 6 and is tightly fitted to the housing 6. Further, the outer ring 16 of the tapered roller bearing 3 is pressed against the inner peripheral surface 6 b on the inner side of the housing 6 and is tightly fitted to the housing 6. The axial end surface 17a of the thick portion 17 of the outer ring 15 and the axial end surface 18a of the thick portion 18 of the outer ring 16 face each other. An annular inner convex portion 20 protruding radially inward of the housing 6 is fitted between the outer rings 15 and 16, and the axial end faces 20 a and 20 b of the inner peripheral convex portion 20 are the outer rings 15. Are in contact with the axial end surface 17a of the outer ring 16 and the axial end surface 18a of the outer ring 16.
[0014]
Since the housing 6 is made of an aluminum alloy, the differential pinion tapered roller bearing device having the above configuration is made of the shaft 1, the tapered roller bearings 2, 3 and the inner ring spacer 5 made of steel. The linear expansion coefficient of the housing 6 is larger than the linear expansion coefficient of the bearings 2 and 3 and the inner ring spacer 5. Specifically, the linear expansion coefficient of the housing 6 is about 20.0 [10 −6 / deg], and the linear expansion coefficients of the shaft 1 and the bearings 2 and 3 are about 11.2 [10 −6 / deg]. is there.
[0015]
Therefore, when the ambient temperature rises, the inner peripheral surface 6a on the outer side of the housing 6 is loosened with respect to the outer ring 15 of the tapered roller bearing 2, and the inner peripheral surface 6b on the inner side of the housing 6 is outer ring 16 of the tapered roller bearing 3. Loose against. This loosening acts in the direction of increasing the axial gaps AC2 and AC3 of the tapered roller bearings 2 and 3. As the contact angle θ1 between the roller 21 and the outer ring 15 is smaller, the increase amount of the axial gap AC2 with respect to the loosening amount is larger, and as the contact angle θ2 between the roller 22 and the outer ring 16 is smaller, the axial gap AC3 with respect to the loosening amount. The amount of increase is large. The contact angle is the inclination angle of the raceway surface of the outer ring with respect to the axial direction.
[0016]
Further, due to the increase in the ambient temperature, the end surface 20a of the inner peripheral convex portion 20 of the housing 6 is tightened against the axial end surface 17a of the thick portion 17 of the outer ring 15 of the tapered roller bearing 2, and the end surface 20b of the inner peripheral convex portion 20 is The tapered roller bearing 3 is tightened against the axial end surface 18 a of the thick portion 18 of the outer ring 16. This tightening works in the direction of reducing the axial gaps AC2 and AC3 between the tapered roller bearings 2 and 3.
[0017]
When the ambient temperature is lowered, the axial gaps AC2 and AC3 are reduced due to the radial tightening of the housing 6 with respect to the outer rings 15 and 16 and the outer rings 15 and 16 of the inner peripheral convex portion 20 of the housing 6 are reduced. The axial gaps AC2 and AC3 increase due to the loosening in the axial direction with respect to 16.
[0018]
As described above, when the ambient temperature changes, there are a factor for increasing the axial gaps AC2 and AC3 and a factor for decreasing the axial gaps. Therefore, the increase factor and the decrease factor are antagonized with each other. By setting the factor, the axial gaps AC2 and AC3 can be prevented from changing when the temperature changes.
[0019]
Specifically, as the above factors, the axial dimension L 0 of the inner circumferential convex portion 20 sandwiched between the two outer rings 15 and 16, the radial allowance D 1 between the outer ring 15 and the housing 6, and the outer ring 16 There is a radial allowance D2 between the housing 6 and the contact angle θ1, θ2. As dimensions L 0 in the axial direction on the inner circumferential protrusion 20 is large, increasing the amount of axial clearance AC2 and AC3 is increased with respect to the increase in the ambient temperature. Moreover, the amount of reduction of the axial gap AC2 with respect to the increase in the ambient temperature increases as the tightening allowance D1 increases. Moreover, the amount of reduction of the axial gap AC3 with respect to the increase in the ambient temperature increases as the tightening allowance D2 increases.
[0020]
Further, as the contact angle θ1 between the roller 21 and the outer ring 15 increases, the increase amount of the axial gap AC2 due to the expansion of the housing 6 in the radial direction (due to an increase in the ambient temperature) decreases. Further, as the contact angle θ2 between the roller 22 and the outer ring 16 is larger, the increase amount of the axial gap AC3 due to the radial expansion of the housing 6 (due to an increase in the ambient temperature) becomes smaller.
[0021]
Thus, for example, to decrease the amount of AC2 and AC3 due to an increase in the axial dimension L 0 of the inner circumferential projection part 20, as increasing amounts of AC2 due to a decrease in interference D1 and D2 and AC3 are substantially equal By setting the above L 0 , D 1, D 2 and the contact angles θ 1 and θ 2, it is possible to prevent the axial gaps AC 2 and AC 3 from changing even if the operating temperature changes. Accordingly, it is possible to prevent the tapered roller bearings 2 and 3 from being insufficiently preloaded or excessively preloaded due to a change in operating temperature. Therefore, according to this embodiment, the housing 6 can be made of an aluminum alloy and reduced in weight without causing play due to insufficient preload or seizure due to excessive preload.
[0022]
Next, the axial dimension L 0 of the peripheral projecting portion 20 sandwiched between the above two outer rings 15 and 16 as the factors, and radial interference D1 of the outer ring 15 and the housing 6, and the outer ring 16 housing 6 A specific set numerical value of the contact angle θ2 and the contact angle θ1 will be described.
[0023]
In this embodiment, the dimension L 0 in the axial direction on the inner circumferential projections 20 and 58 mm, the interference D1 and 31Myuemu～80myuemu, was the interference D2 and 31～80Myuemu. Furthermore, the contact angle θ1 was 20 °, and the contact angle θ2 was 20 °. FIG. 2 shows fluctuation values of the axial gaps AC2 and AC3 with respect to a change in ambient temperature (0 ° C. to 120 ° C.) of the tapered roller bearing device of this embodiment. In the fluctuation range of the axial gap as shown in FIG. 2, there is no play due to insufficient preload, and there is no seizure due to excessive preload.
[0024]
In the above embodiment, the axial dimension L 0 of the convex portion 20 is 58 mm, the fastening allowance D1 is 31 to 80 μm, the fastening allowance D2 is 31 to 80 μm, the contact angle θ1 is 20 °, and the contact angle Although θ2 is set to 20 °, the dimension L 0 in the axial direction of the convex portion 20 satisfies the following expression (1), and the fastening allowances D1 and D2 satisfy the following expression (2). It is only necessary that the angles θ1 and θ2 satisfy the following expression (3). By setting in this way, the fluctuation amount of the axial gaps AC2 and AC3 with respect to the change in the ambient temperature described above can be suppressed to a value that does not cause insufficient preload or excessive preload. When even one of the above formulas (1), (2), and (3) is not satisfied, it has been experimentally found that the preload is insufficient or the preload is excessive. The clearance reduction rate Ke for fitting between the outer ring and the housing was selected to be 0.2 to 0.3.
[0025]
40 mm ≦ L 0 ≦ 60 mm (1)
18 ° ≦ θ ≦ 25 ° ……… (2)
30 μm ≦ D ≦ 80 μm (3)
【The invention's effect】
As is clear from the above, the tapered roller bearing device of the differential pinion of the invention of claim 1 includes a shaft, two tapered roller bearings fitted to the shaft at a predetermined interval in the axial direction, and one of the tapered roller bearings. An inner ring spacer fitted between the inner ring of the tapered roller bearing and the inner ring of the other tapered roller bearing; fitted to the outer circumferential surface of one outer ring and the outer circumferential surface of the other outer ring; A tapered pinion bearing device for a differential pinion comprising a housing including an inner peripheral convex portion that abuts against an axial end face of one outer ring and an axial end face of the other outer ring between the outer ring and the other outer ring. Is made of aluminum alloy, while the inner ring spacer and the two tapered roller bearings are made of steel, and when the operating temperature changes up and down, it is caused by the increase or decrease of the axial dimension of the housing The above tapered roller shaft The amount of increase / decrease in the axial clearance is offset by the increase / decrease amount in the axial clearance of the tapered roller bearing caused by the increase / decrease in the radial dimension of the housing. Further, an axial dimension L 0 of the inner peripheral convex portion, a contact angle θ between the roller of the tapered roller bearing and the outer ring, and a radial tightening margin D between the outer ring and the housing are set.
[0026]
Therefore, according to the first aspect of the present invention, the housing can be made of an aluminum alloy and can be reduced in weight without causing the preload of the tapered roller bearing to be insufficient or excessively preloaded due to the change in operating temperature.
[0027]
According to a second aspect of the present invention, in the tapered roller bearing device of the differential pinion according to the first aspect, the axial dimension L 0 of the housing, the contact angle θ, and the tightening allowance D are expressed by the following formula (1): And a range that satisfies the expressions (2) and (3).
[0028]
40 mm ≦ L 0 ≦ 60 mm (1)
18 ° ≦ θ ≦ 25 ° ……… (2)
30 μm ≦ D ≦ 80 μm (3)
According to the second aspect of the present invention, the amount of change in the axial gap of the tapered roller bearing with respect to the change in ambient temperature can be suppressed to a value that does not cause insufficient preload or excessive preload.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of an essential part of an embodiment of a tapered roller bearing device of a differential pinion according to the present invention.
FIG. 2 is a characteristic diagram showing a change amount of an axial gap with respect to a change in ambient temperature in the embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Shaft, 2, 3 ... Tapered roller bearing, 5 ... Inner ring spacer, 6 ... Housing,
6a, 6b ... inner peripheral surface, 7 ... small diameter part, 8 ... large diameter part, 10, 12 ... inner ring,
11 ... Small diameter part, 11a ... Axial end surface, 13 ... Small diameter part,
13a ... Axial end face, 15, 16 ... Outer ring, 17 ... Thick part,
17a ... Axial end face, 18 ... Thick part, 18a ... Axial end face,
20 ... inner peripheral convex part, 21, 22 ... roller.

Claims (2)

軸と、軸方向に所定の間隔を隔てて上記軸に嵌合されている２つの円すいころ軸受と、一方の円すいころ軸受の内輪と他方の円すいころ軸受の内輪との間に嵌合された内輪間座と、一方の外輪の外周面と他方の外輪の外周面に嵌合されており、かつ、一方の外輪と他方の外輪の間で、一方の外輪の軸方向の端面と他方の外輪の軸方向の端面とに当接する内周凸部を含んだハウジングとを備えたデフピニオンの円すいころ軸受装置において、
上記ハウジングがアルミ合金で作製されている一方、上記内輪間座と２つの円すいころ軸受とが鋼で作製されていて、
使用温度が上下に変化したときに、上記ハウジングの軸方向寸法の増減に起因する上記円すいころ軸受のアキシャル隙間の減増量を、上記ハウジングの径方向寸法の増減に起因する上記円すいころ軸受のアキシャル隙間の増減量でもって相殺するように、上記ハウジングの内の上記２つの外輪の端面に挟まれた内周凸部の軸方向寸法Ｌ０と、上記円すいころ軸受のころと外輪との接触角θと、外輪とハウジングとの径方向の締め代Ｄとが設定されていることを特徴とするデフピニオンの円すいころ軸受装置。Fitted between a shaft, two tapered roller bearings fitted to the shaft at a predetermined interval in the axial direction, and an inner ring of one tapered roller bearing and an inner ring of the other tapered roller bearing The inner ring spacer is fitted to the outer peripheral surface of one outer ring and the outer peripheral surface of the other outer ring, and between the outer ring and the other outer ring, the axial end surface of one outer ring and the other outer ring In a tapered roller bearing device of a differential pinion, comprising a housing including an inner peripheral convex portion that abuts against an axial end face of
While the housing is made of an aluminum alloy, the inner ring spacer and the two tapered roller bearings are made of steel,
When the service temperature changes up and down, the amount of increase in the axial clearance of the tapered roller bearing caused by the increase or decrease of the axial dimension of the housing is the same as the axial amount of the tapered roller bearing caused by the increase or decrease of the radial dimension of the housing. The axial dimension L 0 of the inner peripheral convex portion sandwiched between the end faces of the two outer rings in the housing, the contact angle θ between the roller of the tapered roller bearing and the outer ring, so as to cancel out with the increase / decrease amount of the gap A tapered roller bearing device for a differential pinion, characterized in that a radial interference allowance D between the outer ring and the housing is set. 請求項１に記載のデフピニオンの円すいころ軸受装置において、
上記ハウジングの軸方向寸法Ｌ０と上記接触角θと上記締め代Ｄとを、次の（１）式と（２）式と（３）式を満足するような範囲に設定したことを特徴とするデフピニオンの円すいころ軸受装置。
４０ｍｍ≦Ｌ０≦６０ｍｍ ……… （１）
１８°≦θ≦２５° ……… （２）
３０μｍ ≦Ｄ≦８０μｍ ……… （３）In the differential pinion tapered roller bearing device according to claim 1,
And characterized in that the axial dimension L 0 and the contact angle θ and the interference D of the housing was set to a range that satisfies the following equation (1) and (2) and (3) Def pinion tapered roller bearing device.
40 mm ≦ L 0 ≦ 60 mm (1)
18 ° ≦ θ ≦ 25 ° ……… (2)
30 μm ≦ D ≦ 80 μm (3)
JP10126496A 1996-04-23 1996-04-23 Defpinion tapered roller bearing device Expired - Fee Related JP3623309B2 (en)

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JP10126496A JP3623309B2 (en) 1996-04-23 1996-04-23 Defpinion tapered roller bearing device

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JP3623309B2 true JP3623309B2 (en) 2005-02-23

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JP2003172345A (en) † 2001-12-07 2003-06-20 Koyo Seiko Co Ltd Axle pinion bearing device and vehicular final reduction gear
JP5891720B2 (en) * 2011-11-09 2016-03-23 日本精工株式会社 Hub unit bearing
FR3029992B1 (en) * 2014-12-12 2017-06-16 Ntn-Snr Roulements BEARING BEARING
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