JP3905281B2 - Hub unit - Google Patents

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Publication number
JP3905281B2
JP3905281B2 JP2000042455A JP2000042455A JP3905281B2 JP 3905281 B2 JP3905281 B2 JP 3905281B2 JP 2000042455 A JP2000042455 A JP 2000042455A JP 2000042455 A JP2000042455 A JP 2000042455A JP 3905281 B2 JP3905281 B2 JP 3905281B2
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JP
Japan
Prior art keywords
rolling bearing
constant velocity
row rolling
velocity joint
double row
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Expired - Fee Related
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JP2000042455A
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Japanese (ja)
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JP2001233008A (en
Inventor
孝爾 嶋
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JTEKT Corp
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JTEKT Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • 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
    • F16C2229/00—Setting preload
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/076—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member

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

Description

【０００１】
【発明の属する技術分野】
本発明は、等速ジョイントを組み込んだハブユニットに関する。
【０００２】
【従来の技術】
本願出願人は、等速ジョイントを組み込んだハブユニットとして図５に示すようなものを考えている。
【０００３】
図例のハブユニット１０１は、複列転がり軸受１０２の内周にＣＶＪ（Ｃｏｎｓｔａｎｔ Ｖｅｌｏｃｉｔｙ Ｊｏｉｎｔ）と呼ばれる等速ジョイント１０３を組み込んだ構成になっており、それらの結合は下記するような形態とされている。
【０００４】
つまり、等速ジョイント１０３の外輪１０３ａの軸方向外端に一体形成される径方向外向きのフランジ１０３ｂを複列転がり軸受１０２の外側内輪１０２ａに対して当接させておき、等速ジョイント１０３の外輪１０３ａの軸方向内端を径方向外向きに屈曲変形させる形態でかしめることによりかしめ部１０４を軸受１０２の内側内輪１０２ｂの内端面に対して押し付ける。
【０００５】
このように等速ジョイント１０３の外輪１０３ａのフランジ１０３ｂとかしめ部１０４とにより、複列転がり軸受１０２の２つの内輪１０２ａ，１０２ｂを軸方向から挟んで結合させている。
【０００６】
なお、複列転がり軸受１０２の外側内輪１０２ａに一体形成されてある径方向外向きのフランジ１０２ｃの外面に対してディスクブレーキ装置のディスクロータ１０５や図示しない車輪があてがわれた状態で取り付けられ、また、複列転がり軸受１０２の外輪１０２ｄに一体形成される径方向外向きのフランジ１０２ｅが車体１０６に対してボルト止めされる。
【０００７】
【発明が解決しようとする課題】
上記従来例では、複列転がり軸受１０２を等速ジョイント１０３のフランジ１０３ｂとかしめ部１０４とで挟持させることにより、両者を結合させるようにしており、等速ジョイント１０３の内輪１０３ｃに対してスプライン嵌合されるシャフト１０７から、複列転がり軸受１０２の外側内輪１０２ａに対して取り付けられる車輪（図示省略）に対する動力伝達は、かしめ荷重を受ける前記２カ所の当接面間の摩擦抵抗でもって行わせるようになっている。
【０００８】
このように周方向に引っ掛かりのない面どうしを軸方向から当接させる形態で結合している構造では、かしめ荷重について複列転がり軸受１０２に対して適正な予圧を付与することを考慮しただけであると、結合強度が不足して等速ジョイント１０３の外輪１０３ａと複列転がり軸受１０２の両内輪１０２ａ，１０２ｂとの間でクリープが発生するおそれがある。これに対して、クリープ防止を考慮してかしめ荷重を強くすると、複列転がり軸受１０２に付与する予圧荷重が必要以上に大きくなり過ぎて軸受寿命を低下させるので好ましくない。ここに改良の余地がある。
【０００９】
このような事情に鑑み、本発明は、ハブユニットにおいて、等速ジョイントと複列転がり軸受とを十分な強度で結合させたうえで、複列転がり軸受に対して適正な予圧を付与できる構造の提供を目的とする。
【００１０】
【課題を解決するための手段】
本発明第１のハブユニットは、複列転がり軸受の内周に等速ジョイントが組み込まれるとともに、複列転がり軸受に備える２つの内輪のうちの一方内輪の軸方向外端に一体形成される径方向外向きのフランジの外面にディスクブレーキ装置のディスクロータおよび車輪があてがわれた状態で取り付けられるもので、等速ジョイントの外輪における軸方向外端に一体形成される径方向外向きのフランジに対して複列転がり軸受の前記一方内輪の外端面が当接させられた状態で、前記等速ジョイントの外輪における軸方向内端が径方向外向きに屈曲変形される形態でかしめられることによりこのかしめ部が前記複列転がり軸受の他方内輪の内端面に対して押し付けられており、前記等速ジョイントの外輪におけるフランジと複列転がり軸受の一方内輪との各当接面に、軸方向から嵌合されて周方向で係合する凹部と凸部が振り分けて設けられている、ことを特徴としている。
【００１１】
本発明第２のハブユニットは、上記第１の構成において、前記等速ジョイントの外輪におけるフランジと複列転がり軸受の一方内輪との各当接面に設けられる凹部および凸部が、それぞれ、円周等間隔に複数設けられる面セレーションとされている、ことを特徴としている。
【００１２】
要するに、本発明では、等速ジョイントの外輪におけるフランジと複列転がり軸受の外側内輪とを凹凸嵌合部分によって回り止めさせる形態にし、かしめ荷重については、単に、複列転がり軸受の２つの内輪を抜け止めさせるとともに、複列転がり軸受に対して適正な予圧を付与させることだけを考慮して管理する形態にしている。
【００１３】
これにより、従来例のようにかしめ荷重を必要以上に強く設定せずとも、等速ジョイントに入力される動力を複列転がり軸受の外側内輪に取り付けられる車輪（図示省略）に対して効率よく確実に伝達させることが可能になる。
【００１４】
【発明の実施の形態】
本発明の詳細を図面に示す実施形態に基づいて説明する。
【００１５】
図１ないし図３は本発明の一実施形態を示している。図１は、ハブユニットの縦断側面図、図２は、図１における等速ジョイントの外輪フランジと複列転がり軸受の外側内輪との結合部分を分離して示す斜視図、図３は、図１のハブユニットの使用形態を示す模式図である。
【００１６】
図例のハブユニット１は、複列外向きアンギュラ玉軸受などの複列転がり軸受２の内周に、等速ジョイント３を組み込んだ構成になっている。
【００１７】
複列外向きアンギュラ玉軸受２は、２つの内輪２１Ａ，２１Ｂと、二列の軌道溝を有する単一の外輪２２と、二列で配設される複数の玉２３と、二つの保持器２４とを備えている。
【００１８】
等速ジョイント３は、一般的に周知のＣＶＪ（Ｃｏｎｓｔａｎｔ Ｖｅｌｏｃｉｔｙ Ｊｏｉｎｔ）と呼ばれるもので、内輪３１と、外輪３２と、複数の玉３３と、保持器３４とを備えている。
【００１９】
そして、複列転がり軸受２の外側内輪２１Ａに一体形成される径方向外向きのフランジ２５の外面に対して、ディスクブレーキ装置のディスクロータ４および車輪（図示省略）があてがわれた状態で取り付けられ、複列転がり軸受２の外輪２２に一体形成される径方向外向きのフランジ２６が車体５などに対してボルト止めされる。また、等速ジョイント３は、図３に示すような形態でシャフト６を介して車両のデファレンシャル装置７に対して連結される。なお、シャフト６は、その軸端が等速ジョイント３の内輪３１に対してスプライン嵌合されて止め輪９などで抜け止め固定される。
【００２０】
これにより、シャフト６の回転動力が、等速ジョイント３の外輪３２を介して複列転がり軸受２の外側内輪２１Ａに取り付けられてある図示しない車輪に対して伝達される。
【００２１】
なお、上記等速ジョイント３は、通常、シャフト６と、シャフト６の他端に取り付けられる等速ジョイント８とでドライブシャフトアッセンブリを構成するものであるが、この実施形態のハブユニット１では、上記等速ジョイント３を組み込んでいるから、ドライブシャフトアッセンブリと合体した製品とすることができる。
【００２２】
ところで、図示例のハブユニット１では、等速ジョイント３の傾動支点を複列転がり軸受２の軸方向中央位置に配置しているが、そのような配置にしていれば、以下のようなメリットがある。まず、等速ジョイント３のトルク伝達時や偶力発生時において複列転がり軸受２に対して曲げモーメントが作用せずに済む。また、図３に示すように、等速ジョイント３がデファレンシャル装置７に対して高低差Ｈを付けた状態で設置される場合について説明する。図３は本実施形態にかかる構造、図４は比較例にかかる構造である。なお、比較例は、ハブユニット１の内側に等速ジョイント３を隣り合わせで付設する従来一般的な構造である。つまり、本実施形態では、等速ジョイント３の傾動支点からシャフト６とデファレンシャル装置７との連結部位までの水平直線距離Ｌ１が比較例のＬ２に比べて長くなって、シャフト６の傾き角度つまりジョイント角度θ１が比較例のθ２に比べて小さくなる。これにより、複列転がり軸受２に対してジョイント角度が要因となる起動力が小さくなって、複列転がり軸受２の寿命向上が可能になる。この他、等速ジョイント３に付設されるブーツ（図示省略）の屈曲量が小さくなって、その破損寿命が向上するというメリットも得られる。
【００２３】
次に、複列転がり軸受２と等速ジョイント３との結合形態を説明する。
【００２４】
等速ジョイント３の外周に複列転がり軸受２を外嵌装着する。このときの嵌め合い形態は、すきま嵌めあるいは中間嵌めでよい。
【００２５】
そして、等速ジョイント３の外輪３２において軸方向外端には、径方向外向きのフランジ３５が設けられており、このフランジ３５に対して複列転がり軸受２の外側内輪２１Ａの外端面を当接させる。この状態で等速ジョイント３の外輪３２における軸方向内端をローリングかしめ方法などにより径方向外向きに屈曲変形させる形態でかしめることにより、このかしめ部３６を複列転がり軸受２の内側内輪２１Ｂの内端面に対して押し付ける。これにより、等速ジョイント３に対して複列転がり軸受２が軸方向で位置決めされて両者が一体的に結合される。
【００２６】
しかも、等速ジョイント３の外輪３２におけるフランジ３５と複列転がり軸受２の外側内輪２１Ａとの各当接面には、軸方向から嵌合して周方向に一体化する凹部と凸部が振り分けて設けられている。
【００２７】
具体的に、図２に示すように、例えばフランジ３５の内面には、周方向等間隔に複数の凸歯３７を配列した雄セレーションが設けられている。一方の外側内輪２１Ａの外端側開口には、大径孔２７が設けられており、この大径孔２７において径方向に沿う面には周方向等間隔に複数の凹溝２８を配列した雌セレーションが設けられており、それらが軸方向から嵌合させられるようになる。
【００２８】
このように、等速ジョイント３の外輪３２におけるフランジ３５と複列転がり軸受２の外側内輪２１Ａとを雄雌の面セレーションによって確実に回り止めさせる形態にし、かしめ荷重については、単に、複列転がり軸受２の２つの内輪２１Ａ，２１Ｂを抜け止めさせるとともに、複列転がり軸受２に対して適正な予圧を付与させることだけを考慮して管理する形態にしている。
【００２９】
これにより、従来例のようにかしめ荷重を必要以上に強く設定せずとも、等速ジョイント３に連結されるシャフト６から複列転がり軸受２の外側内輪２１Ａに取り付けられる車輪（図示省略）に対して効率よく確実に動力伝達させることが可能になる。
【００３０】
なお、本発明は上記実施形態のみに限定されるものではなく、種々な応用や変形が考えられる。
【００３１】
例えば、上記実施形態では、等速ジョイント３の外輪３２と複列転がり軸受２の外側内輪２１Ａとの当接面に設ける凹部や凸部について雄雌の面セレーションとした例を挙げているが、凹部や凸部を円周上の少なくとも１カ所に１組だけ設けるようにしたものも本発明に含まれる。
【００３２】
【発明の効果】
請求項１および２の発明では、等速ジョイントの外輪におけるフランジと複列転がり軸受の外側内輪とを凹凸嵌合部分によって回り止めさせる形態にし、かしめ荷重については、単に、複列転がり軸受の２つの内輪を抜け止めさせるとともに、複列転がり軸受に対して適正な予圧を付与させることだけを考慮して管理する形態にしている。
【００３３】
これにより、従来例のようにかしめ荷重を必要以上に強く設定せずとも、等速ジョイントに入力される動力を複列転がり軸受の外側内輪に取り付けられる車輪（図示省略）に対して効率よく確実に伝達させることが可能になる。
【００３４】
したがって、本発明では、等速ジョイントを組み込んだハブユニットについて、等速ジョイントと複列転がり軸受との結合を強固にできて、しかも、複列転がり軸受に対して適正な予圧を付与できるようになり、信頼性の高い製品を提供できるようになる。
【図面の簡単な説明】
【図１】本発明の一実施形態にかかるハブユニットの縦断側面図
【図２】図１における等速ジョイントの外輪フランジと複列転がり軸受の外側内輪との当接面を引き離して示す斜視図
【図３】図１のハブユニットの使用形態を示す模式図
【図４】本実施形態に対する比較例の使用形態を示す模式図
【図５】従来例にかかるハブユニットの縦断側面図
【符号の説明】
１ ハブユニット
２ 複列転がり軸受
３ 等速ジョイント
４ ディスクロータ
２１Ａ 複列転がり軸受２の外側内輪
２１Ｂ 複列転がり軸受２の内側内輪
２５ 外側内輪２１Ａのフランジ
２８ フランジ２５の凹溝
３２ 等速ジョイント３の外輪
３５ 外輪３２のフランジ
３６ 外輪３２のかしめ部
３７ フランジ３５の凸歯[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a hub unit incorporating a constant velocity joint.
[0002]
[Prior art]
The applicant of the present application considers a hub unit incorporating a constant velocity joint as shown in FIG.
[0003]
The hub unit 101 shown in the figure has a structure in which a constant velocity joint 103 called CVJ (Constant Velocity Joint) is incorporated in the inner periphery of the double row rolling bearing 102, and the coupling thereof is configured as follows. Yes.
[0004]
That is, a radially outward flange 103b integrally formed at the axial outer end of the outer ring 103a of the constant velocity joint 103 is brought into contact with the outer inner ring 102a of the double row rolling bearing 102 so that the constant velocity joint 103 The caulking portion 104 is pressed against the inner end surface of the inner inner ring 102b of the bearing 102 by caulking the inner end in the axial direction of the outer ring 103a so as to bend and deform radially outward.
[0005]
Thus, the flange 103b of the outer ring 103a of the constant velocity joint 103 and the caulking portion 104 couple the two inner rings 102a and 102b of the double row rolling bearing 102 so as to be sandwiched from the axial direction.
[0006]
The disc rotor 105 of the disc brake device and a wheel (not shown) are attached to the outer surface of the radially outward flange 102c formed integrally with the outer inner ring 102a of the double row rolling bearing 102. Further, a radially outward flange 102e formed integrally with the outer ring 102d of the double row rolling bearing 102 is bolted to the vehicle body 106.
[0007]
[Problems to be solved by the invention]
In the above conventional example, the double row rolling bearing 102 is sandwiched between the flange 103b of the constant velocity joint 103 and the caulking portion 104 so as to be coupled to each other, and the spline fitting is performed on the inner ring 103c of the constant velocity joint 103. The power transmission from the combined shaft 107 to the wheel (not shown) attached to the outer inner ring 102a of the double row rolling bearing 102 is performed by the frictional resistance between the two contact surfaces receiving the caulking load. It is like that.
[0008]
In such a structure in which the surfaces that are not caught in the circumferential direction are joined in a form in which they are brought into contact with each other in the axial direction, only an appropriate preload is applied to the double row rolling bearing 102 with respect to the caulking load. If so, there is a risk that creep will occur between the outer ring 103 a of the constant velocity joint 103 and the inner rings 102 a and 102 b of the double row rolling bearing 102 due to insufficient coupling strength. On the other hand, if the caulking load is increased in consideration of the prevention of creep, the preload applied to the double row rolling bearing 102 becomes unnecessarily large and the bearing life is reduced. There is room for improvement here.
[0009]
In view of such circumstances, the present invention has a structure in which an appropriate preload can be applied to the double row rolling bearing after the constant velocity joint and the double row rolling bearing are coupled with sufficient strength in the hub unit. For the purpose of provision.
[0010]
[Means for Solving the Problems]
In the first hub unit of the present invention, a constant velocity joint is incorporated in the inner periphery of the double row rolling bearing, and the diameter is integrally formed at the outer end in the axial direction of one inner ring of two inner rings provided in the double row rolling bearing. It is attached with the disc rotor and wheels of the disc brake device applied to the outer surface of the outwardly facing flange, and is a radially outward flange that is formed integrally with the axially outer end of the outer ring of the constant velocity joint. On the other hand, when the outer end surface of the one inner ring of the double row rolling bearing is in contact with the outer ring, the axial inner end of the outer ring of the constant velocity joint is caulked in a form that is bent and deformed radially outward. The caulking portion is pressed against the inner end face of the other inner ring of the double row rolling bearing, and one of the flange and the double row rolling bearing in the outer ring of the constant velocity joint Each contact surface between the wheels, recesses and projections which engage in fitted with circumferentially from the axial direction is provided by distributing, and wherein a.
[0011]
In the second hub unit of the present invention, in the first configuration described above, the concave portion and the convex portion provided on each contact surface between the flange of the outer ring of the constant velocity joint and one inner ring of the double-row rolling bearing are respectively circular. It is characterized by a plurality of surface serrations provided at equal circumferential intervals.
[0012]
In short, in the present invention, the flange in the outer ring of the constant velocity joint and the outer inner ring of the double row rolling bearing are prevented from rotating by the concave-convex fitting portion. In addition to preventing it from falling off, it is managed in consideration of only giving an appropriate preload to the double row rolling bearing.
[0013]
As a result, the power input to the constant velocity joint can be efficiently and reliably applied to the wheels (not shown) attached to the outer ring of the double row rolling bearing without setting the caulking load stronger than necessary as in the conventional example. Can be transmitted to.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
The details of the present invention will be described based on embodiments shown in the drawings.
[0015]
1 to 3 show an embodiment of the present invention. FIG. 1 is a longitudinal side view of a hub unit, FIG. 2 is a perspective view showing a joint portion between an outer ring flange of a constant velocity joint and an outer inner ring of a double-row rolling bearing in FIG. 1, and FIG. It is a schematic diagram which shows the usage condition of this hub unit.
[0016]
The hub unit 1 shown in the figure has a configuration in which a constant velocity joint 3 is incorporated on the inner periphery of a double row rolling bearing 2 such as a double row outward angular ball bearing.
[0017]
The double-row outward angular ball bearing 2 includes two inner rings 21A and 21B, a single outer ring 22 having two rows of raceway grooves, a plurality of balls 23 arranged in two rows, and two cages 24. And.
[0018]
The constant velocity joint 3 is generally called CVJ (Constant Velocity Joint), and includes an inner ring 31, an outer ring 32, a plurality of balls 33, and a cage 34.
[0019]
Then, the disc rotor 4 and the wheel (not shown) of the disc brake device are attached to the outer surface of the radially outward flange 25 formed integrally with the outer inner ring 21A of the double row rolling bearing 2. Then, a radially outward flange 26 formed integrally with the outer ring 22 of the double-row rolling bearing 2 is bolted to the vehicle body 5 and the like. Moreover, the constant velocity joint 3 is connected with respect to the differential apparatus 7 of a vehicle through the shaft 6 in the form as shown in FIG. The shaft 6 has a shaft end that is spline-fitted to the inner ring 31 of the constant velocity joint 3 and is fixed by a retaining ring 9 or the like.
[0020]
Thereby, the rotational power of the shaft 6 is transmitted to the wheel (not shown) attached to the outer inner ring 21A of the double row rolling bearing 2 via the outer ring 32 of the constant velocity joint 3.
[0021]
The constant velocity joint 3 normally constitutes a drive shaft assembly with the shaft 6 and the constant velocity joint 8 attached to the other end of the shaft 6. In the hub unit 1 of this embodiment, Since the constant velocity joint 3 is incorporated, a product combined with the drive shaft assembly can be obtained.
[0022]
By the way, in the hub unit 1 of the illustrated example, the tilting fulcrum of the constant velocity joint 3 is arranged at the center position in the axial direction of the double-row rolling bearing 2. is there. First, a bending moment does not act on the double row rolling bearing 2 when torque is transmitted to the constant velocity joint 3 or when a couple is generated. Moreover, as shown in FIG. 3, the case where the constant velocity joint 3 is installed in the state which attached the height difference H with respect to the differential apparatus 7 is demonstrated. FIG. 3 shows a structure according to this embodiment, and FIG. 4 shows a structure according to a comparative example. The comparative example has a conventional general structure in which the constant velocity joint 3 is provided adjacent to each other inside the hub unit 1. That is, in this embodiment, the horizontal linear distance L1 from the tilting fulcrum of the constant velocity joint 3 to the connecting portion of the shaft 6 and the differential device 7 is longer than L2 of the comparative example, and the inclination angle of the shaft 6, that is, the joint The angle θ1 is smaller than θ2 of the comparative example. As a result, the starting force caused by the joint angle with respect to the double row rolling bearing 2 is reduced, and the life of the double row rolling bearing 2 can be improved. In addition, the amount of bending of the boot (not shown) attached to the constant velocity joint 3 is reduced, and the merit that the breakage life is improved is also obtained.
[0023]
Next, the coupling | bonding form of the double row rolling bearing 2 and the constant velocity joint 3 is demonstrated.
[0024]
A double-row rolling bearing 2 is fitted on the outer periphery of the constant velocity joint 3. The fitting form at this time may be a clearance fit or an intermediate fit.
[0025]
A radially outward flange 35 is provided at the outer end 32 in the axial direction of the outer ring 32 of the constant velocity joint 3, and the outer end surface of the outer inner ring 21 </ b> A of the double row rolling bearing 2 is abutted against the flange 35. Make contact. In this state, the caulking portion 36 is caulked in a form in which the axial inner end of the outer ring 32 of the constant velocity joint 3 is bent and deformed radially outward by a rolling caulking method or the like. Press against the inner edge of the. Thereby, the double row rolling bearing 2 is positioned with respect to the constant velocity joint 3 in the axial direction, and the both are integrally coupled.
[0026]
In addition, a concave portion and a convex portion that are fitted from the axial direction and integrated in the circumferential direction are distributed to each contact surface between the flange 35 in the outer ring 32 of the constant velocity joint 3 and the outer inner ring 21A of the double row rolling bearing 2. Is provided.
[0027]
Specifically, as shown in FIG. 2, for example, the inner surface of the flange 35 is provided with a male serration in which a plurality of convex teeth 37 are arranged at equal intervals in the circumferential direction. A large-diameter hole 27 is provided in the outer end side opening of one outer inner ring 21A, and a plurality of concave grooves 28 are arranged on the surface along the radial direction in the large-diameter hole 27 at equal intervals in the circumferential direction. Serrations are provided so that they can be fitted from the axial direction.
[0028]
In this manner, the flange 35 in the outer ring 32 of the constant velocity joint 3 and the outer inner ring 21A of the double row rolling bearing 2 are reliably prevented from rotating by male and female surface serrations, and the caulking load is simply double row rolling. The two inner rings 21 </ b> A and 21 </ b> B of the bearing 2 are prevented from coming off and managed in consideration of only applying an appropriate preload to the double-row rolling bearing 2.
[0029]
Thereby, with respect to a wheel (not shown) attached to the outer inner ring 21A of the double row rolling bearing 2 from the shaft 6 connected to the constant velocity joint 3 without setting the caulking load stronger than necessary as in the conventional example. Power can be transmitted efficiently and reliably.
[0030]
In addition, this invention is not limited only to the said embodiment, Various application and deformation | transformation can be considered.
[0031]
For example, in the above embodiment, an example is given in which male and female surface serrations are provided for the concave portions and convex portions provided on the contact surface between the outer ring 32 of the constant velocity joint 3 and the outer inner ring 21A of the double row rolling bearing 2. A configuration in which only one set of concave and convex portions is provided at least at one location on the circumference is also included in the present invention.
[0032]
【The invention's effect】
According to the first and second aspects of the present invention, the flange in the outer ring of the constant velocity joint and the outer inner ring of the double row rolling bearing are prevented from rotating by the concave-convex fitting portion, and the caulking load is simply 2 of the double row rolling bearing. The inner ring is prevented from coming off and is managed in consideration of only giving an appropriate preload to the double row rolling bearing.
[0033]
As a result, the power input to the constant velocity joint can be efficiently and reliably applied to the wheels (not shown) attached to the outer ring of the double row rolling bearing without setting the caulking load stronger than necessary as in the conventional example. Can be transmitted to.
[0034]
Therefore, in the present invention, for a hub unit incorporating a constant velocity joint, the coupling between the constant velocity joint and the double row rolling bearing can be strengthened, and an appropriate preload can be applied to the double row rolling bearing. It becomes possible to provide highly reliable products.
[Brief description of the drawings]
FIG. 1 is a longitudinal side view of a hub unit according to an embodiment of the present invention. FIG. 2 is a perspective view showing a contact surface between an outer ring flange of a constant velocity joint and an outer inner ring of a double row rolling bearing in FIG. 3 is a schematic diagram showing a usage pattern of the hub unit of FIG. 1. FIG. 4 is a schematic diagram showing a usage pattern of a comparative example with respect to the present embodiment. FIG. 5 is a vertical side view of a hub unit according to a conventional example. Explanation】
DESCRIPTION OF SYMBOLS 1 Hub unit 2 Double row rolling bearing 3 Constant velocity joint 4 Disc rotor 21A Outer inner ring 21B of double row rolling bearing 2 Inner inner ring 25 of double row rolling bearing 2 Flange 28 of outer inner ring 21A Concave groove 32 of flange 25 Constant velocity joint 3 Outer ring 35 Flange 36 of outer ring 32 Caulking portion 37 of outer ring 32 Convex teeth of flange 35

Claims (2)

複列転がり軸受の内周に等速ジョイントが組み込まれるとともに、複列転がり軸受に備える２つの内輪のうちの一方内輪の軸方向外端に一体形成される径方向外向きのフランジの外面にディスクブレーキ装置のディスクロータおよび車輪があてがわれた状態で取り付けられるハブユニットであって、
等速ジョイントの外輪における軸方向外端に一体形成される径方向外向きのフランジに対して複列転がり軸受の前記一方内輪の外端面が当接させられた状態で、前記等速ジョイントの外輪における軸方向内端が径方向外向きに屈曲変形される形態でかしめられることによりこのかしめ部が前記複列転がり軸受の他方内輪の内端面に対して押し付けられており、
前記等速ジョイントの外輪におけるフランジと複列転がり軸受の一方内輪との各当接面に、軸方向から嵌合されて周方向で係合する凹部と凸部が振り分けて設けられている、ことを特徴とするハブユニット。A constant velocity joint is incorporated in the inner periphery of the double row rolling bearing, and a disk is formed on the outer surface of the radially outward flange formed integrally with the axial outer end of one of the two inner rings provided in the double row rolling bearing. A hub unit mounted with the disc rotor and wheels of the brake device applied thereto,
The outer ring of the constant velocity joint in a state where the outer end surface of the one inner ring of the double row rolling bearing is in contact with a radially outward flange formed integrally with the outer end of the constant velocity joint in the axial outer end. The caulking portion is pressed against the inner end surface of the other inner ring of the double row rolling bearing by caulking the inner end in the axial direction in a form that is bent and deformed radially outward.
A concave portion and a convex portion that are fitted from the axial direction and engaged in the circumferential direction are provided separately on the contact surfaces of the flange in the outer ring of the constant velocity joint and one inner ring of the double row rolling bearing. Hub unit characterized by. 請求項１記載のハブユニットにおいて、
前記等速ジョイントの外輪におけるフランジと複列転がり軸受の一方内輪との各当接面に設けられる凹部および凸部が、それぞれ、円周等間隔に複数設けられる面セレーションとされている、ことを特徴とするハブユニット。The hub unit according to claim 1, wherein
The concave and convex portions provided on the contact surfaces of the flange in the outer ring of the constant velocity joint and the one inner ring of the double row rolling bearing are each a surface serration provided in a plurality at equal circumferential intervals. Features hub unit.
JP2000042455A 2000-02-21 2000-02-21 Hub unit Expired - Fee Related JP3905281B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2000042455A JP3905281B2 (en) 2000-02-21 2000-02-21 Hub unit

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Publication Number Publication Date
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JP3905281B2 true JP3905281B2 (en) 2007-04-18

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022043959A1 (en) * 2020-08-31 2022-03-03 Ree Automotive Ltd. Wheel-drive assembly

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022043959A1 (en) * 2020-08-31 2022-03-03 Ree Automotive Ltd. Wheel-drive assembly
US11332005B2 (en) 2020-08-31 2022-05-17 Ree Automotive Ltd. Wheel-drive assembly
US11667192B2 (en) 2020-08-31 2023-06-06 Ree Automotive Ltd Wheel-drive assembly
GB2614827A (en) * 2020-08-31 2023-07-19 Ree Automotive Ltd Wheel-drive assembly

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