JP2005003111A - Rolling bearing device - Google Patents

Rolling bearing device Download PDF

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Publication number
JP2005003111A
JP2005003111A JP2003167770A JP2003167770A JP2005003111A JP 2005003111 A JP2005003111 A JP 2005003111A JP 2003167770 A JP2003167770 A JP 2003167770A JP 2003167770 A JP2003167770 A JP 2003167770A JP 2005003111 A JP2005003111 A JP 2005003111A
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Japan
Prior art keywords
angle
outer peripheral
large collar
bearing device
rolling bearing
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JP2003167770A
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JP4013836B2 (en
Inventor
Hisanobu Nakamura
久信 中村
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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
    • 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
    • F16C33/64—Special methods of manufacture
    • 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
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To prevent quenching crack by restricting local overheat in high frequency hardening. <P>SOLUTION: In this rolling bearing device 1, comprising tapered rollers 5 and 6 as rolling elements, a tapered track part 33 is formed at an outer circumferential part of an inner ring member (hub shaft) 3, and a large flange part 34 to guide a larger end surface of the tapered roller 5 is formed on the larger diameter side of the track part 33. The angle θ formed by a guide surface 34a and an outer circumferential surface 34b in the large flange part 34 is set as an obtuse angle, so that an outer circumferential angular part of the large flange part 34 does not make a sharp edge, while its volume is increased. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、円すいころを使用する転がり軸受装置に関する。
【０００２】
【従来の技術】
円すいころを使用する転がり軸受装置は、自動車の車輪支持用のほか、各種の機械装置の回転部材の支持に使用されている。
【０００３】
図５を参照して、自動車の車輪支持用としての転がり軸受装置２１を説明すると、この転がり軸受装置２１は、外輪２２と、ハブ軸２３と、内輪２４と、２組の円すいころ２５，２６とを備えており、複列円すいころ軸受タイプとなっている。
【０００４】
ハブ軸２３には、その軸方向一方側に、車輪を取り付けるためのハブフランジ２３ａが一体に形成され、軸方向他方側の小径部２３ｂには、内輪２４が嵌着されている。
【０００５】
さらに、ハブ軸２３には、前記ハブフランジ２３ａ寄りの外周部に、円すいころ２５に対応して、ハブフランジ２３ａの側に向けてテーパ状に広がる軌道部２７が形成されるとともに、この軌道部２７の大径側に大鍔部２８が形成されている。この大鍔部２８の軌道部２７側の面が、円すいころ２５の大端面を案内する案内面２８ａとなっている。
【０００６】
従来、この種の転がり軸受装置では、大鍔部２８の案内面２８ａが軌道部２７に向けて傾斜しているのに対して、大鍔部２８の外周面２８ｂは軸方向とほぼ平行になって、案内面２８ａと外周面２８ｂとの角部は、鋭角の角度γとなっている（例えば、特許文献１参照。）。
【０００７】
【特許文献１】
特開２０００−２２５１号公報
【０００８】
【発明が解決しようとする課題】
上記転がり軸受装置２１の場合、ハブフランジ２３ａの付け根辺りから大鍔部２８、さらに軌道部２７から小径部２３ｂにかけて局部的な高周波焼き入れを施して、図中のクロスハッチングで示す硬化層２３ｃを形成して、軌道部２７の性能確保を図っている。
【０００９】
しかしながら、この高周波熱焼き入れに際しては、大鍔部２８の外周角部、すなわち、大鍔部２８の案内面２８ａと外周面２８ｂとに囲まれた部分は、鋭角のエッジとなっているので、この部分に誘導電流が過度に集中して、過熱状態となり、大鍔部２８の近傍で焼き割れが生じるおそれがあり、最終製造工程を経た製品に対して全数検査をすることなどが要求されていた。
【００１０】
したがって、本発明は、大鍔部の構造に改良を加えることで高周波焼き入れに際しての大鍔部での焼き割れをなくした転がり軸受装置を提供することを、解決すべき課題としている。
【００１１】
【課題を解決するための手段】
本発明は、外輪部材の内径側に複数の円すいころを介して回転可能に支持される内輪部材を備え、前記内輪部材の外周部に形成されるテーパ状の軌道部の大径側に、円すいころの大端面を案内する案内面を備えた大鍔部が形成され、前記内輪部材の外周部の少なくとも軌道部と大鍔部とを含む部分の表面には、高周波焼き入れによる硬化層が形成されている転がり軸受装置において、前記大鍔部の外周面とその案内面とがなす角度を鈍角に設定したことにより、上述した課題を達成している。
【００１２】
本発明の転がり軸受装置は、自動車の車輪支持用転がり軸受装置（ハブユニット）に好ましく適用することができるが、その用途はこれに限定されるものではなく、各種の機械装置の回転部材の支持に適用可能である。ハブユニットに適用した場合、前記内輪部材はハブ軸に相当する。ハブユニットとしては、駆動輪用、従動輪用を問わない。
【００１３】
上記構成において、内輪部材の外周部の大鍔部等を含む部分を、高周波焼き入れにより局部的に硬化処理する際、大鍔部の外周角部は、鈍角の角部となっているから、従来のようにエッジ効果により誘導電流が過度に集中することがない。また、大鍔部の外周角部は、鈍角となることで、体積が増大していて熱容量が大きい。そのため、大鍔部には局部的な過熱が起こらず、焼き割れの発生が防止もしくは抑制できるようになった。
【００１４】
なお、大鍔部の外周面と案内面とは、互いに接するまで延長している必要はなく、大鍔部の案内面と外周面とで構成される大鍔部の外周角部は、先端が面取り加工されていてもよいし、丸みを有するよう湾曲加工されていてもよい。
【００１５】
本発明の望ましい実施形態としては、大鍔部の外周面とその案内面とがなす角度を、前記案内面と軸方向に平行な線とがなす対軸線角度に２０°を加えた角度を越え、かつ前記対軸線角度に９０°を加えた角度を越えない範囲とした実施形態が挙げられる。
【００１６】
大鍔部の案内面と外周面との角度が、前記の角度範囲を下回る角度である場合、高周波焼入れの仕方の違い、たとえば、高周波コイルと大鍔部との間隔が狭い、等の違いによっては、大鍔部の外周角部が過熱することがあり、所期通りの焼き割れ防止の効果が得られなくなる。大鍔部の案内面と外周面との角度が、前記の角度範囲を上回る角度である場合、大鍔部の外周面の立ち上がり角度が急峻になりすぎ、大鍔部の近傍の構造を、従来とは大幅に異なる形に変更する必要が生じ、実用的ではない。
【００１７】
最も望ましい実施形態は、大鍔部の案内面と外周面とのなす角度が、対軸線角度よりも、２５°〜４５°大きい角度範囲に含まれている場合である。
【００１８】
この実施形態では、焼き割れ防止効果が確実となるほか、大鍔部等の加熱部分の温度が平均化し、均質の硬化層が得られる。また、大鍔部とその近傍の形状が大幅に変化しないので、大鍔部の近傍に設けられるシールについては、従来通りのシールが使用できる。
【００１９】
さらに、自動車の車輪支持用転がり軸受装置（ハブユニット）である場合、大鍔部の外周面は、ハブフランジに向けてテーパ状に広がることになるが、この外周面を、凹凸や段落部なしにハブフランジまで延長することができ、形状が単純化することで、それだけ内輪部材（ハブ軸）の製造が容易になる。
【００２０】
【発明の実施の形態】
以下、本発明の実施形態に係る転がり軸受装置を、図面を参照して詳細に説明する。図１ないし図３は、本発明の一実施形態に係り、図１は転がり軸受装置の縦断側面図、図２は、図１の要部であるハブ軸の拡大断面図、図３は、図１のハブ軸のさらなる拡大断面図である。図１の右側は車両インナー側を、また、左側は車両アウター側を示す。
【００２１】
本実施形態の転がり軸受装置１は、外輪２と、内輪部材としてのハブ軸３と、内輪４と、２組の円すいころ５，６と、ボルト７と、保持器８，９と、シール１０，１１とを備えており、複列円すいころ軸受タイプとなっている。
【００２２】
外輪２は、内周に複列に軌道部２ａ，２ｂを有し、外周部には突部２ｃが形成され、この突部２ｃを介して車体側の部材に取り付けられる。
【００２３】
ハブ軸３は、外輪２の内径側に円すいころ５，６を介して回転可能に支持されるもので、軸部３１と、この軸部３１の軸方向一方側（車体アウター側）から径方向外向きに延出するハブフランジ３２と、インロー部３６とからなる。図示しないブレーキ装置のディスクロータや駆動輪の車輪は、ハブフランジ３２とインロー部３６に対してボルト７で固定される。
【００２４】
ハブ軸３の軸部３１は、中心部に軸方向に貫通する軸孔３１ａを有し、この軸孔３１ａには、駆動軸（図示せず）がスプライン嵌合される。軸部３１の軸方向他方側（車体インナー側）には小径部３１ｂがあって、この小径部３１ｂに前記内輪４が嵌着されている。
【００２５】
小径部３１ｂとハブフランジ３２の間で、軸部３１の外周には、一方の組の円すいころ５に対応して、ハブフランジ３２側に向けてテーパ状に広がる軌道部３３が形成されている。さらに、軌道部３３の大径側に、円すいころ５の大端面を案内する案内面３４ａを有する大鍔部３４が形成されている。なお、符号３５は、大鍔部３４の案内面３４ａと軌道部３３との入隅部に形成された逃げ溝である。
【００２６】
軸部３１の軌道部３３と、これと径方向に対向する外輪２の一方の軌道部２ａとの間に一組の円すいころ５が配置され、外輪２の他方の軌道部２ｂと内輪４の軌道部との間に、他の組の円すいころ６が配置されている。保持器８，９は、各組の円すいころ５，６を保持している。シール１０，１１は、外輪２の軸方向両端に設けられている。
【００２７】
軸部３１の外周各部のうち、大鍔部３４から小径部３１ｂに至る領域には、高周波焼き入れにより、クロスハッチングで示す硬化層３１ｃが形成されている。高周波焼き入れにより、軸部３１の表面部は、８００〜９００℃程度に加熱され、硬化される。軸部３１は、この高周波焼き入れ後に、２００℃程度の低温で焼き戻しされる。
【００２８】
図２および図３を参照して本実施形態の特徴を説明すると、本実施形態では、大鍔部３４の外周角部３４ｃの内角を鈍角に設定して、外周角部３４ｃから尖鋭なエッジ形状をなくすとともに、その角部３４ｃの体積を増大させている。
【００２９】
従来では、大鍔部３４の外周面３４ｂは、その直径が一様、つまり軸方向に平行な線Ｐに沿うか、あるいはその線Ｐよりも車両アウター側に向けて１０°程度の勾配でテーパ状に直径が増大する程度のもので、大鍔部３４の案内面３４ａと外周面３４ｂとがなす角度が鋭角になっていた。
【００３０】
これに対して、本実施形態における大鍔部３４の案内面３４ａと外周面３４ｂとのなす角度θを鈍角に設定したことに特徴を有している。
【００３１】
この場合の角度θは、具体的には、次式（１）で示すように、大鍔部３４の案内面３４ａが軸方向に平行な線Ｐに対してなす角度α（この明細書では、対軸線角度という）に２０°を加えた角度β１を越えた鈍角から、この対軸線角度αに９０°を加えた角度β２を越えない鈍角の範囲に含まれていることが好ましい。
【００３２】
α＋２０°＜θ＜α＋９０° …（１）
図示の例の場合、大鍔部３４の案内面３４ａと外周面３４ｂとのなす角度θは、対軸線角度αよりも３０°程度大きい鈍角に設定されている。
【００３３】
なお、大鍔部３４の外周面３４ｂは、軸方向に対して一定の角度を保って、ハブフランジ３０の内側面にまで延長しており、ハブフランジ３０の手前に凹凸や段落部は形成されていないことが好ましい。
【００３４】
上記構成によれば、大鍔部３４の外周角部３４ｃ、すなわち、大鍔部３４の案内面３４ａと外周面３４ｂとに囲まれた部分は、鈍角の角部となっているから、この大鍔部３４等を含む部分を高周波焼き入れにより局部的に硬化させる際、エッジ効果が抑制されるか、生じにくくなる。また、大鍔部３４の外周角部３４ｃは体積が増大して熱容量が大きくなるから、大鍔部３４に局部的な過熱が起きるような可能性が大幅に低減し、高周波焼き入れの応力による焼き割れの発生が、従来よりも大きく低減されるか、あるいは全く防止されるようになる。
【００３５】
なお、図示のように、大鍔部３４の案内面３４ａと外周面３４ｂとのなす角度θが、対軸線角度αよりも３０°程度大きい角度に設定されていると、高周波焼き入れの仕方に影響されず、確実に焼き割れ防止効果が得られるほか、大鍔部３４等の焼き入れ部分の温度が平均化し、均質の硬化層が得られる。また、大鍔部３４の外周面３４ｂの立ち上がり角度は急峻ではないので、近傍に設けられるシール１０については、従来通りのシールが使用できる。さらに、大鍔部３４の外周面３４ｂは、凹凸や段落部なしにハブフランジ３２まで延長することができ、ハブ軸３の形状が単純化する。
【００３６】
本発明は、図４に示すように、円すいころを使用する他のタイプの転がり軸受装置に実施することができる。図４は、本発明の他の実施形態に係る転がり軸受装置のハブ軸の縦断側面図で、ハブ軸以外の構成部分は、鎖線で示している。
【００３７】
この実施形態の転がり軸受装置は、従動輪用で、ハブ軸３の軸部３１は中実になっている。大鍔部３４の案内面３４ａと外周面３４ｂとのなす角度θが、鈍角になっている点を含め、他の構成は、図１ないし図３の実施形態と同じである。
【００３８】
本発明は、上記のほか、各種の機械装置の回転部材の支持用として、たとえば、圧延機のロールネック用や、鉄道車両の駆動装置用として適用可能である。
【００３９】
【発明の効果】
本発明によれば、大鍔部の案内面と外周面とに囲まれる外周角部が尖鋭なエッジを形成しないので、局部的な高周波焼き入れによる硬化処理で、焼き割れの発生することが防止もしくは抑制することができる。
【図面の簡単な説明】
【図１】本発明の一実施形態に係る転がり軸受装置の縦断側面図
【図２】図１の要部の拡大断面図
【図３】図１の要部のさらなる拡大断面図
【図４】本発明の他の実施形態に係る転がり軸受装置のハブ軸の縦断側面図
【図５】従来の転がり軸受装置のハブ軸の縦断側面図
【符号の説明】
２ 外輪 ３ ハブ軸（内輪部材）
５，６ 円すいころ
３３ 軌道部
３４ 大鍔部 ３４ａ 案内面 ３４ｂ 外周面
θ 角度（大鍔部の案内面と外周面との間）[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rolling bearing device that uses tapered rollers.
[0002]
[Prior art]
Rolling bearing devices using tapered rollers are used for supporting rotating members of various mechanical devices in addition to supporting wheels of automobiles.
[0003]
Referring to FIG. 5, a rolling bearing device 21 for supporting automobile wheels will be described. The rolling bearing device 21 includes an outer ring 22, a hub shaft 23, an inner ring 24, and two sets of tapered rollers 25 and 26. It is a double row tapered roller bearing type.
[0004]
A hub flange 23a for attaching a wheel is integrally formed on one side in the axial direction of the hub shaft 23, and an inner ring 24 is fitted on a small diameter portion 23b on the other side in the axial direction.
[0005]
Further, the hub shaft 23 is formed with a raceway portion 27 extending in a taper shape toward the hub flange 23a side corresponding to the tapered roller 25 on the outer peripheral portion near the hub flange 23a. A large collar portion 28 is formed on the large diameter side of 27. The surface of the large collar portion 28 on the track portion 27 side is a guide surface 28 a that guides the large end surface of the tapered roller 25.
[0006]
Conventionally, in this type of rolling bearing device, the guide surface 28a of the large collar portion 28 is inclined toward the raceway portion 27, whereas the outer peripheral surface 28b of the large collar portion 28 is substantially parallel to the axial direction. The corners of the guide surface 28a and the outer peripheral surface 28b are acute angles γ (see, for example, Patent Document 1).
[0007]
[Patent Document 1]
Japanese Patent Laid-Open No. 2000-2251
[Problems to be solved by the invention]
In the case of the rolling bearing device 21, local induction hardening is performed from the base of the hub flange 23a to the large collar portion 28, and further from the raceway portion 27 to the small diameter portion 23b, so that a hardened layer 23c indicated by cross hatching in the figure is formed. By forming, the performance of the track part 27 is secured.
[0009]
However, at the time of this induction hardening, the outer peripheral corner portion of the large collar portion 28, that is, the portion surrounded by the guide surface 28a and the outer peripheral surface 28b of the large collar portion 28 is an acute edge, Inductive currents are excessively concentrated in this part, resulting in an overheated state, and there is a risk of burning cracks in the vicinity of the large collar portion 28, and it is required to inspect all products that have undergone the final manufacturing process. It was.
[0010]
Accordingly, an object of the present invention is to provide a rolling bearing device that eliminates burning cracks in the large collar part during induction hardening by improving the structure of the large collar part.
[0011]
[Means for Solving the Problems]
The present invention includes an inner ring member that is rotatably supported via a plurality of tapered rollers on the inner diameter side of the outer ring member, and the tapered ring is formed on the larger diameter side of the tapered raceway portion formed on the outer periphery of the inner ring member. A large collar portion having a guide surface for guiding the large end surface of the roller is formed, and a hardened layer is formed by induction hardening on the surface of at least the outer circumferential portion of the inner ring member including the raceway portion and the large collar portion. In the rolling bearing device that is used, the above-described problem is achieved by setting the angle formed by the outer peripheral surface of the large collar portion and the guide surface thereof to an obtuse angle.
[0012]
The rolling bearing device of the present invention can be preferably applied to a rolling bearing device (hub unit) for supporting a wheel of an automobile, but the application is not limited to this, and the rotating member of various mechanical devices is supported. It is applicable to. When applied to a hub unit, the inner ring member corresponds to a hub shaft. The hub unit may be used for driving wheels or driven wheels.
[0013]
In the above configuration, when the part including the large collar part of the outer peripheral part of the inner ring member is locally hardened by induction hardening, the outer peripheral corner part of the large collar part is an obtuse corner part, The induced current is not excessively concentrated by the edge effect as in the prior art. Further, the outer peripheral corner portion of the large collar portion becomes an obtuse angle, so that the volume is increased and the heat capacity is large. For this reason, local overheating does not occur in the large collar, and the occurrence of burning cracks can be prevented or suppressed.
[0014]
The outer peripheral surface and the guide surface of the large collar portion do not need to be extended until they contact each other, and the outer peripheral corner of the large collar portion constituted by the guide surface and the outer peripheral surface of the large collar portion has a tip at the end. It may be chamfered or may be curved so as to have a roundness.
[0015]
In a preferred embodiment of the present invention, the angle formed by the outer peripheral surface of the large collar and the guide surface exceeds the angle obtained by adding 20 ° to the opposite axis angle formed by the guide surface and a line parallel to the axial direction. And an embodiment in which the angle obtained by adding 90 ° to the opposite axis angle is not exceeded.
[0016]
When the angle between the guide surface and the outer peripheral surface of the large collar is less than the above angle range, due to the difference in the method of induction hardening, for example, the difference between the high frequency coil and the large collar is narrow, etc. However, the outer peripheral corner of the large collar may overheat, and the desired effect of preventing burning cracks cannot be obtained. When the angle between the guide surface of the large collar part and the outer peripheral surface is an angle exceeding the above-mentioned angle range, the rising angle of the outer peripheral surface of the large collar part becomes too steep, and the structure in the vicinity of the large collar part is It is necessary to change to a very different form, and is not practical.
[0017]
The most desirable embodiment is a case where the angle formed by the guide surface of the large collar and the outer peripheral surface is included in an angle range that is 25 ° to 45 ° larger than the opposite axis angle.
[0018]
In this embodiment, the effect of preventing burning cracks is ensured, and the temperature of the heated portion such as the large collar portion is averaged to obtain a uniform hardened layer. Moreover, since the shape of the large collar part and its vicinity does not change significantly, the conventional seal can be used for the seal provided in the vicinity of the large collar part.
[0019]
Furthermore, in the case of a rolling bearing device for supporting a wheel of an automobile (hub unit), the outer peripheral surface of the large collar portion is tapered toward the hub flange, but this outer peripheral surface has no irregularities or paragraphs. The inner ring member (hub shaft) can be manufactured more easily by simplifying the shape.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a rolling bearing device according to an embodiment of the present invention will be described in detail with reference to the drawings. 1 to 3 relate to one embodiment of the present invention, FIG. 1 is a longitudinal side view of a rolling bearing device, FIG. 2 is an enlarged sectional view of a hub shaft which is a main part of FIG. 1, and FIG. It is the further expanded sectional view of 1 hub axle. The right side of FIG. 1 shows the vehicle inner side, and the left side shows the vehicle outer side.
[0021]
The rolling bearing device 1 of this embodiment includes an outer ring 2, a hub shaft 3 as an inner ring member, an inner ring 4, two sets of tapered rollers 5, 6, bolts 7, cages 8 and 9, and a seal 10. , 11 and is a double row tapered roller bearing type.
[0022]
The outer ring 2 has raceways 2a and 2b in double rows on the inner periphery, and a protrusion 2c is formed on the outer periphery, and is attached to a member on the vehicle body side via the protrusion 2c.
[0023]
The hub shaft 3 is rotatably supported on the inner diameter side of the outer ring 2 via tapered rollers 5, 6. The hub portion 3 is radially extended from the shaft portion 31 and one axial direction side (the vehicle body outer side) of the shaft portion 31. It consists of a hub flange 32 extending outward and an inlay portion 36. A disk rotor and a wheel of a driving wheel (not shown) of the brake device are fixed to the hub flange 32 and the spigot portion 36 with bolts 7.
[0024]
The shaft portion 31 of the hub shaft 3 has a shaft hole 31a penetrating in the axial direction at the center, and a drive shaft (not shown) is spline fitted into the shaft hole 31a. There is a small diameter portion 31b on the other axial side (vehicle body inner side) of the shaft portion 31, and the inner ring 4 is fitted to the small diameter portion 31b.
[0025]
Between the small diameter portion 31 b and the hub flange 32, a raceway portion 33 is formed on the outer periphery of the shaft portion 31 so as to taper toward the hub flange 32 side corresponding to one set of tapered rollers 5. . Furthermore, a large collar portion 34 having a guide surface 34 a for guiding the large end surface of the tapered roller 5 is formed on the large diameter side of the raceway portion 33. Reference numeral 35 denotes a relief groove formed at the corner between the guide surface 34 a of the large collar portion 34 and the track portion 33.
[0026]
A pair of tapered rollers 5 is disposed between the raceway portion 33 of the shaft portion 31 and the one raceway portion 2a of the outer ring 2 opposed to the raceway in the radial direction, and the other raceway portion 2b of the outer ring 2 and the inner race 4 Another set of tapered rollers 6 is disposed between the raceway portions. The cages 8 and 9 hold each set of tapered rollers 5 and 6. The seals 10 and 11 are provided at both axial ends of the outer ring 2.
[0027]
A hardened layer 31c indicated by cross-hatching is formed by induction hardening in a region from the large collar portion 34 to the small diameter portion 31b in each outer peripheral portion of the shaft portion 31. By induction hardening, the surface portion of the shaft portion 31 is heated to about 800 to 900 ° C. and cured. The shaft portion 31 is tempered at a low temperature of about 200 ° C. after the induction hardening.
[0028]
The features of this embodiment will be described with reference to FIGS. 2 and 3. In this embodiment, the inner angle of the outer peripheral corner portion 34 c of the large collar portion 34 is set to an obtuse angle, and a sharp edge shape is formed from the outer peripheral corner portion 34 c. And the volume of the corner 34c is increased.
[0029]
Conventionally, the outer peripheral surface 34b of the large collar portion 34 is uniform in diameter, that is, along a line P parallel to the axial direction, or tapered with a gradient of about 10 ° toward the vehicle outer side from the line P. The angle formed by the guide surface 34a of the large collar portion 34 and the outer peripheral surface 34b is an acute angle.
[0030]
On the other hand, the present embodiment is characterized in that the angle θ formed by the guide surface 34a and the outer peripheral surface 34b of the large collar portion 34 in the present embodiment is set to an obtuse angle.
[0031]
Specifically, the angle θ in this case is an angle α (in this specification, an angle α formed by the guide surface 34a of the large collar portion 34 with respect to a line P parallel to the axial direction, as shown in the following equation (1). the 20 ° angle beta 1 from obtuse beyond that added to) that pair axis line angle, is preferably contained in the range of obtuse angle not exceeding the angle beta 2 plus 90 ° to the pair axis line angle alpha.
[0032]
α + 20 ° <θ <α + 90 ° (1)
In the case of the illustrated example, the angle θ formed between the guide surface 34a and the outer peripheral surface 34b of the large collar portion 34 is set to an obtuse angle that is approximately 30 ° larger than the counter-axis angle α.
[0033]
The outer peripheral surface 34b of the large collar portion 34 extends to the inner surface of the hub flange 30 at a constant angle with respect to the axial direction, and irregularities and paragraphs are formed in front of the hub flange 30. Preferably not.
[0034]
According to the above configuration, the outer peripheral corner portion 34c of the large collar portion 34, that is, the portion surrounded by the guide surface 34a and the outer peripheral surface 34b of the large collar portion 34 is an obtuse corner portion. When the portion including the flange portion 34 and the like is locally hardened by induction hardening, the edge effect is suppressed or hardly generated. Further, since the outer corner portion 34c of the large collar portion 34 increases in volume and heat capacity increases, the possibility that local overheating occurs in the large collar portion 34 is greatly reduced, and due to the stress of induction hardening. Generation | occurrence | production of a burning crack is reduced greatly compared with the past, or comes to be prevented at all.
[0035]
As shown in the figure, when the angle θ formed between the guide surface 34a of the large collar 34 and the outer peripheral surface 34b is set to an angle that is approximately 30 ° larger than the opposite axis angle α, the induction hardening is performed. Without being influenced, the effect of preventing cracking can be obtained with certainty, and the temperature of the quenched portion such as the large collar portion 34 can be averaged to obtain a uniform hardened layer. Further, since the rising angle of the outer peripheral surface 34b of the large collar portion 34 is not steep, a conventional seal can be used for the seal 10 provided in the vicinity. Furthermore, the outer peripheral surface 34b of the large collar portion 34 can be extended to the hub flange 32 without unevenness or a stepped portion, and the shape of the hub shaft 3 is simplified.
[0036]
As shown in FIG. 4, the present invention can be implemented in other types of rolling bearing devices that use tapered rollers. FIG. 4 is a longitudinal side view of a hub shaft of a rolling bearing device according to another embodiment of the present invention, and components other than the hub shaft are indicated by chain lines.
[0037]
The rolling bearing device of this embodiment is for a driven wheel, and the shaft portion 31 of the hub shaft 3 is solid. Other configurations are the same as those in the embodiment of FIGS. 1 to 3, including that the angle θ formed by the guide surface 34 a and the outer peripheral surface 34 b of the large collar 34 is an obtuse angle.
[0038]
In addition to the above, the present invention can be applied as a support for rotating members of various mechanical devices, for example, as a roll neck of a rolling mill or a drive device of a railway vehicle.
[0039]
【The invention's effect】
According to the present invention, since the outer peripheral corner surrounded by the guide surface and outer peripheral surface of the large collar does not form a sharp edge, it is possible to prevent the occurrence of baking cracks in the hardening process by local induction hardening. Or it can be suppressed.
[Brief description of the drawings]
1 is a longitudinal side view of a rolling bearing device according to an embodiment of the present invention. FIG. 2 is an enlarged cross-sectional view of the main part of FIG. 1. FIG. 3 is a further enlarged cross-sectional view of the main part of FIG. FIG. 5 is a longitudinal side view of a hub shaft of a rolling bearing device according to another embodiment of the present invention. FIG. 5 is a longitudinal side view of a hub shaft of a conventional rolling bearing device.
2 Outer ring 3 Hub axle (inner ring member)
5,6 Tapered roller 33 Track 34 Large collar 34a Guide surface 34b Outer peripheral surface θ angle (between the guide surface and outer peripheral surface of large collar)

Claims (2)

外輪部材の内径側に複数の円すいころを介して回転可能に支持される内輪部材を備え、前記内輪部材の外周部に形成されるテーパ状の軌道部の大径側に、円すいころの大端面を案内する案内面を備えた大鍔部が形成され、前記内輪部材の外周部の少なくとも軌道部と大鍔部とを含む部分の表面には、高周波焼き入れによる硬化層が形成されている転がり軸受装置において、
前記大鍔部の外周面とその案内面とがなす角度を鈍角に設定した、転がり軸受装置。An inner ring member rotatably supported via a plurality of tapered rollers is provided on the inner diameter side of the outer ring member, and a large end surface of the tapered roller is disposed on the large diameter side of the tapered raceway portion formed on the outer peripheral portion of the inner ring member. A rolling part having a hardened layer formed by induction hardening is formed on the surface of a part including at least the raceway part and the large collar part of the outer peripheral part of the inner ring member. In the bearing device,
A rolling bearing device in which an angle formed between an outer peripheral surface of the large collar portion and a guide surface thereof is set to an obtuse angle. 前記大鍔部の外周面とその案内面とがなす角度を、前記案内面と軸方向に平行な線とがなす対軸線角度に２０°を加えた角度を越え、かつ前記対軸線角度に９０°を加えた角度を越えない範囲とした、請求項１に記載の転がり軸受装置。The angle formed between the outer peripheral surface of the large collar portion and the guide surface exceeds the angle obtained by adding 20 ° to the opposite axis angle formed by the guide surface and a line parallel to the axial direction, and the angle between the opposite axis is 90. The rolling bearing device according to claim 1, wherein the rolling bearing device is within a range that does not exceed an angle added with °.
JP2003167770A 2003-06-12 2003-06-12 Rolling bearing device Expired - Fee Related JP4013836B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008223973A (en) * 2007-03-15 2008-09-25 Jtekt Corp Tapered roller bearing device
JP2008256020A (en) * 2007-04-02 2008-10-23 Jtekt Corp Sealing structure of rolling bearing device for wheel

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100494429C (en) * 2005-05-20 2009-06-03 东北轻合金有限责任公司 Manufacturing method of ultrahard aluminium alloy

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008223973A (en) * 2007-03-15 2008-09-25 Jtekt Corp Tapered roller bearing device
US9051964B2 (en) 2007-03-15 2015-06-09 Jtekt Corporation Tapered roller bearing apparatus and hub unit
JP2008256020A (en) * 2007-04-02 2008-10-23 Jtekt Corp Sealing structure of rolling bearing device for wheel

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