JP3821979B2 - Axle bearing device - Google Patents

Axle bearing device Download PDF

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Publication number
JP3821979B2
JP3821979B2 JP04873099A JP4873099A JP3821979B2 JP 3821979 B2 JP3821979 B2 JP 3821979B2 JP 04873099 A JP04873099 A JP 04873099A JP 4873099 A JP4873099 A JP 4873099A JP 3821979 B2 JP3821979 B2 JP 3821979B2
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Japan
Prior art keywords
ring member
track
outer ring
diameter
raceway
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JP04873099A
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Japanese (ja)
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JP2000211308A (en
Inventor
基司 河村
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JTEKT Corp
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • 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
    • F16C19/185—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 two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • 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
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • 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

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

Description

【０００１】
【発明の属する技術分野】
この発明は、例えば自動車の車輪に使用される車軸用軸受装置に関する。
【０００２】
【従来の技術】
従来の車軸用軸受装置としては、図４のものが知られている。この軸受装置は、内周面に第一軌道４６及び第二軌道４７が形成された一体形の外輪部材４０と、外輪部材４０の上記二列の軌道４６，４７に配装された転動体４４，４５を介して相対回転可能に上記外輪部材４０内に配置された内輪部材４３と、内輪部材４３の軸端部４３ａ及び反軸端部４３ｂに嵌合固定され上記各転動体４４，４５が転動する軌道４８，４９が形成された二個の内輪４１，４２とを有し、上記外輪部材４０の軸端部４３ａ側に位置する第一軌道４６にほぼ対応する外輪部材４０外周面に車体側に固定される径方向外方フランジ５０が形成されるとともに、内輪部材４３の反軸端部４３ｂで車輪側に固定される径方向外方フランジ５１が形成されている。なお、上記内輪４１，４２は、必ず必要ではなく、内輪４１，４２の両方あるいは片方を省き、内輪部材４３に直接、転動体４４，４５が転動する軌道を形成してもよい。また、各転動体４４，４５は、保持器５２，５３にて円周方向等間隔に保持されている。５４，５５は、軸受の外輪部材４０の両端部内周面に嵌合固定され内輪４１，４２に摺接して軸受内部を密封するシールである。さらに、転動体列４４側の軸受部Ａと、転動体列４５側の軸受部Ｂは、その作用線Ｆ１，Ｆ２が外輪部材４０の外周面側で交差する構成のアンギュラ玉軸受部である。そして、外輪部材４０の第一軌道４６の肩部５６と第二軌道４７の肩部５７、すなわち両軌道４６，４７間の内周面４０ａは同一径の平坦面に形成されている。
【０００３】
【発明が解決しようとする課題】
上記の従来の車軸用軸受装置においては、内輪回転形式であるため、インナー側（内輪部材４３の軸端部４３ａ側）は、通常、負荷荷重が大きいため転動体４４が外輪４０の第一軌道４６からの肩乗り上げが生じにくく、逆にアウター側（内輪部材４３の反軸端部４３ｂ側）は、負荷荷重が小さいため転動体４５が外輪４０の第二軌道４７からの肩乗り上げが生じやすい。従って、各外輪軌道４６，４７における各肩部５６，５７内周面寸法は、アウター側にある外輪４０の第二軌道４７の検討により設計され、この設計と同じ設計にてインナー側の外輪軌道４６および肩部５６を形成している。このため、インナー側の肩部５６の設計は余裕のある設計となっているのが、現状である。
【０００４】
ところで、転動体４４，４５の転動上、内、外輪４１，４２，４０の各軌道４６，４７，４８，４９は例えば、高周波焼入れにて所定硬度が付与されている。しかし、上述のように、内輪回転形式であることから、車体側に取付けられる外輪部材４０の外周面のフランジ５０は、外輪部材４０の第一軌道４６にほぼ対応する位置に形成されているため、外輪部材４０の両軌道４６，４７に高周波焼入れを行うと、フランジ５０に近い第一軌道４６側は熱が奪われやすく、すなわち軌道４６に焼きが入りにくくなる。このため、比較的強めの条件で焼入れを行うことが多く、このようにすると、第一軌道４６から肩部５６にかけてのエッジ部５８に熱が集中して組織が悪化しやすく、欠けの原因につながることのないように十分な管理が要求される。
【０００５】
そこで、この発明は、内輪部材の軸端部側の外輪部材の第一軌道の肩部設計が余裕をもって行われていることに着目し、第一軌道から肩部にかけての部分での熱集中を避けて組織の悪化を確実に防止できる車軸用軸受装置を提供することを目的としている。
【０００６】
【課題を解決するための手段】
上記課題を解決するための手段として、請求項１においては、負荷荷重の大きいインナー側の内周面に第一軌道が形成され、負荷荷重の小さいアウター側の内周面に上記第一軌道と最外径が同じ第二軌道が形成された一体形の外輪部材と、外輪部材の上記二列の軌道に配装された転動体を介して相対回転可能に上記外輪部材内に配置された内輪部材と、上記外輪部材の第一軌道にほぼ対応する外輪部材外周面に車体側に固定される径方向外方フランジが形成され、上記第二軌道よりも上記第一軌道がより強く高周波焼入れされる車軸用軸受装置において、上記外輪部材の第一軌道から肩部にかけてのエッジ部に面取り部が形成され、上記外輪部材の第ニ軌道から肩部にかけてのエッジ部には面取り部が形成されていないことを特徴とする。
【０００７】
さらに、請求項２においては、負荷荷重の大きいインナー側の内周面に第一軌道が形成され、負荷荷重の小さいアウター側の内周面に上記第一軌道と最外径が同じ第二軌道が形成された一体形の外輪部材と、外輪部材の上記二列の軌道に配装された転動体を介して相対回転可能に上記外輪部材内に配置された内輪部材と、上記外輪部材の第一軌道にほぼ対応する外輪部材外周面に車体側に固定される径方向外方フランジが形成され、上記第二軌道よりも上記第一軌道がより強く高周波焼入れされる車軸用軸受装置において、上記外輪部材の第一軌道と第二軌道の間の内周面が、第一軌道に連なり内輪部材の軸線に平行な大径の平坦面と、第二軌道に連なり内輪部材の軸線に平行な小径の平坦面と、上記大径の平坦面と上記小径の平坦面との間で両平坦面を結合する結合面とから構成され、第一軌道の最外径と上記大径の平坦面の内径Ｄ２との差が、第二軌道の最外径と上記小径の平坦面の内径Ｄ１との差よりも小さく設定されていることを特徴とする。
【０００８】
【発明の実施の形態】
以下、この発明の具体的実施の形態について図面を参照して説明する。 図１において、この発明の車軸用軸受装置は、内周面に第一軌道７及び第二軌道８が形成された一体形の外輪部材１と、外輪部材１の上記二列の軌道７，８に配装された転動体５，６を介して相対回転可能に上記外輪部材１内に配置された内輪部材４と、内輪部材４の軸端部４ａ及び反軸端部４ｂに嵌合固定され上記各転動体５，６が転動する軌道９，１０が形成された二個の内輪２，３とを有し、上記外輪部材１の軸端部４ａ側に位置する第一軌道７にほぼ対応する外輪部材１の外周面に車体側に固定される径方向外方フランジ１１が形成されるとともに、内輪部材４の反軸端部４ｂで車輪側に固定される径方向外方フランジ１２が形成されている。なお、上記内輪２，３は、必ず必要ではなく、内輪２，３の両方あるいは片方を省き、内輪部材４に直接、転動体５，６が転動する軌道を形成してもよい。また、各転動体５，６は、保持器１３，１４にて円周方向等間隔に保持されている。１５，１６は、軸受の外輪部材１の両端部内周面に嵌合固定され内輪２，３に摺接して軸受内部を密封するシールである。さらに内輪２，３は軸端部４に螺合されたナット２３で固定されている。
【０００９】
さらに、転動体５側の軸受部Ａと、転動体６側の軸受部Ｂは、その作用線Ｆ１，Ｆ２が外輪部材１の外周面側で交差する構成のアンギュラ玉軸受である。そして、外輪部材１の第一軌道７の肩部１７と第二軌道８の肩部１８、すなわち両軌道間７，８の内周面１９は、第一軌道７に連なる大径部と第二軌道８に連なる小径部とから構成されている。
【００１０】
上記肩部１７，１８の関係については、具体的実施形態の一つとして、 図１および 図２が挙げられる。すなわち、外輪部材１の第一軌道７から肩部１７にかけてＲ面取り部１９が形成され、このＲ面取り部１９から第二軌道８まで肩部１８を含み、内周面が内輪部材４の軸線にほぼ平行な平坦面２０とされている。なお、このＲ面取り部１９の代わりにＣ面取り部等としてもよく、少なくとも面取り部であればよい。外輪部材１の上記内周面形状は、面取り部を従来構造に付加することでよいため、加工が容易である。
【００１１】
さらに、図３は別の実施形態である。外輪部材１の第一軌道７と第二軌道８間の内周面が、第一軌道７に連なる肩部１７に形成された内輪部材４の軸線にほぼ平行な大径Ｄ２の平坦面２１と、第二軌道８に連なる肩部１８に形成された内輪部材４の軸線にほぼ平行な小径Ｄ１の平坦面２２と、両平坦面２１，２２を結合する斜面２３とから形成されている。すなわち、Ｄ２＞Ｄ１の関係にある。この構成とすることにより、焼入れ時の冷却水が供給しやすくなる。
【００１２】
本各実施形態において、第一軌道の肩部内径が大きくなるが、従来技術において説明したように、余裕のある設計がされていることから、性能上、問題はない。
【００１３】
【発明の効果】
本発明では、第一軌道から肩部にかけてのエッジ部に面取り部が形成されているか、あるいは、第一軌道に連なる部分が、第二軌道に連なる部分より大径とされている。従って、第一軌道から肩部にかけてのエッジ部の突出量が従来に比べて緩和されるため、焼入れ時のエッジ部に熱が集中しにくく、組織の悪化が防止できる。
【図面の簡単な説明】
【 図１】本発明の一実施形態の車軸用軸受装置の断面図である。
【図２】図１の要部拡大図である。
【 図３】本発明の別の実施形態の車軸用軸受装置の断面図である。
【 図４】従来の車軸用軸受装置の断面図である。
【符号の説明】
１ 外輪部材
４ 内輪部材
４ａ 軸端部
４ｂ 反軸端部
５ 転動体
６ 転動体
７ 第一軌道
８ 第二軌道[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an axle bearing device used for, for example, an automobile wheel.
[0002]
[Prior art]
As a conventional axle bearing device, the one shown in FIG. 4 is known. The bearing device includes an integrated outer ring member 40 having a first raceway 46 and a second raceway 47 formed on an inner peripheral surface, and rolling elements 44 arranged on the two rows of raceways 46 and 47 of the outer ring member 40. 45, the inner ring member 43 disposed in the outer ring member 40 so as to be rotatable relative to the inner ring member 40, and the shaft end portion 43a and the non-shaft end portion 43b of the inner ring member 43. The outer ring member 40 has two inner rings 41 and 42 formed with rolling raceways 48 and 49, and the outer ring member 40 has an outer peripheral surface substantially corresponding to the first raceway 46 positioned on the shaft end portion 43 a side of the outer ring member 40. A radially outward flange 50 fixed to the vehicle body side is formed, and a radially outward flange 51 fixed to the wheel side is formed at the countershaft end portion 43 b of the inner ring member 43. The inner rings 41 and 42 are not necessarily required, and both or one of the inner rings 41 and 42 may be omitted, and a raceway on which the rolling elements 44 and 45 roll directly may be formed on the inner ring member 43. The rolling elements 44 and 45 are held at equal intervals in the circumferential direction by the cages 52 and 53. Reference numerals 54 and 55 denote seals that are fitted and fixed to the inner peripheral surfaces of both ends of the outer ring member 40 of the bearing and are in sliding contact with the inner rings 41 and 42 to seal the inside of the bearing. Furthermore, the bearing portion A on the rolling element row 44 side and the bearing portion B on the rolling element row 45 side are angular ball bearing portions having a configuration in which their action lines F <b> 1 and F <b> 2 intersect on the outer peripheral surface side of the outer ring member 40. The shoulder portion 56 of the first raceway 46 and the shoulder portion 57 of the second raceway 47 of the outer ring member 40, that is, the inner peripheral surface 40a between the raceways 46 and 47 are formed as flat surfaces having the same diameter.
[0003]
[Problems to be solved by the invention]
In the conventional axle bearing device described above, since it is an inner ring rotating type, the inner side (the shaft end portion 43a side of the inner ring member 43) is usually heavily loaded, so that the rolling element 44 is the first track of the outer ring 40. 46 on the outer side (on the opposite end 43b side of the inner ring member 43) is less likely to cause the rolling element 45 to ride on the shoulder from the second raceway 47 of the outer ring 40. . Accordingly, the inner peripheral surface dimensions of the shoulders 56 and 57 in the outer ring raceways 46 and 47 are designed by examining the second raceway 47 of the outer ring 40 on the outer side, and the inner side outer ring raceway is designed in the same design as this design. 46 and a shoulder 56 are formed. For this reason, the present situation is that the design of the shoulder portion 56 on the inner side has a margin.
[0004]
By the way, on the rolling of the rolling elements 44 and 45, the raceways 46, 47, 48, and 49 of the inner and outer rings 41, 42, and 40 are given predetermined hardness by, for example, induction hardening. However, as described above, because of the inner ring rotation type, the flange 50 on the outer peripheral surface of the outer ring member 40 attached to the vehicle body side is formed at a position substantially corresponding to the first track 46 of the outer ring member 40. When induction hardening is performed on both the tracks 46 and 47 of the outer ring member 40, the first track 46 side close to the flange 50 is easily deprived of heat, that is, the track 46 is hard to be hardened. For this reason, quenching is often performed under relatively strong conditions, and in this case, heat concentrates on the edge portion 58 from the first track 46 to the shoulder portion 56, and the structure is likely to deteriorate, resulting in chipping. Sufficient management is required so as not to be connected.
[0005]
Therefore, the present invention pays attention to the fact that the shoulder design of the first track of the outer ring member on the shaft end side of the inner ring member is performed with a margin, and concentrates heat in the portion from the first track to the shoulder. An object of the present invention is to provide an axle bearing device that can avoid the deterioration of the structure with certainty.
[0006]
[Means for Solving the Problems]
As means for solving the above-mentioned problems, in claim 1, a first track is formed on the inner peripheral surface of the inner side having a large load, and the first track is formed on the inner peripheral surface of the outer side having a small load. An integral outer ring member having a second raceway having the same outermost diameter and an inner ring disposed in the outer ring member so as to be relatively rotatable via rolling elements disposed on the two rows of raceways of the outer ring member. And a radially outer flange fixed to the vehicle body on the outer ring member outer circumferential surface substantially corresponding to the first raceway of the outer race member, and the first raceway is hardened by induction hardening more strongly than the second raceway. in the bearing device for that axle, cut edge to the edge portion of the over the shoulder from the first raceway of the outer ring member is formed, the chamfered portion is formed on the edge portion of the over the shoulder from the second raceway of the outer ring member It is characterized by not .
[0007]
Further, in claim 2, a first track is formed on the inner peripheral surface of the inner side having a large load, and the second track having the same outermost diameter as the first track on the inner peripheral surface of the outer side having a small load. And an inner ring member disposed in the outer ring member so as to be relatively rotatable via rolling elements disposed on the two rows of raceways of the outer ring member, and a first of the outer ring member substantially corresponding to the radial outward flange that is fixed to the vehicle body to the outer ring member outer peripheral surface is formed on one track, in a bearing apparatus for an axle the first trajectory is more strongly induction hardening than the second track, the upper The inner peripheral surface between the first track and the second track of the outer ring member is connected to the first track and has a large-diameter flat surface parallel to the axis of the inner ring member, and to the second track and parallel to the axis of the inner ring member. between the small-diameter flat surface, the flat surface and the smaller diameter of the flat surface of the large diameter It is composed of a coupling surface for coupling the two flat surfaces, uppermost difference between the outer diameter and the inner diameter D2 of the flat surface of the large diameter, the inner diameter of the flat surface of the outermost diameter and the smaller diameter of the second track of the first track It is characterized by being set smaller than the difference from D1.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. In FIG. 1, the axle bearing device of the present invention includes an integrated outer ring member 1 having a first track 7 and a second track 8 formed on the inner peripheral surface, and the two rows of tracks 7, 8 of the outer ring member 1. Are fitted and fixed to the inner ring member 4 disposed in the outer ring member 1 so as to be relatively rotatable via the rolling elements 5 and 6 arranged on the shaft, and the shaft end 4a and the non-shaft end 4b of the inner ring member 4. It has two inner rings 2, 3 formed with raceways 9, 10 on which the rolling elements 5, 6 roll, and the first raceway 7 located on the side of the shaft end 4 a of the outer ring member 1 is almost A radial outer flange 11 fixed to the vehicle body side is formed on the outer peripheral surface of the corresponding outer ring member 1, and a radial outer flange 12 fixed to the wheel side at the opposite end 4 b of the inner ring member 4 is formed. Is formed. The inner rings 2 and 3 are not necessarily required, and both or one of the inner rings 2 and 3 may be omitted to form a track on which the rolling elements 5 and 6 roll directly on the inner ring member 4. The rolling elements 5 and 6 are held at equal intervals in the circumferential direction by the cages 13 and 14. Reference numerals 15 and 16 denote seals that are fitted and fixed to the inner peripheral surfaces of both end portions of the outer ring member 1 of the bearing and slidably contact the inner rings 2 and 3 to seal the inside of the bearing. Further, the inner rings 2 and 3 are fixed by a nut 23 screwed to the shaft end 4.
[0009]
Further, the bearing part A on the rolling element 5 side and the bearing part B on the rolling element 6 side are angular ball bearings having their action lines F1 and F2 intersecting on the outer peripheral surface side of the outer ring member 1. The shoulder portion 17 of the first track 7 and the shoulder portion 18 of the second track 8 of the outer ring member 1, that is, the inner peripheral surface 19 between the two tracks 7, 8, A small-diameter portion continuous with the track 8 is formed.
[0010]
As for the relationship between the shoulder portions 17 and 18, FIG. 1 and FIG. 2 can be cited as one specific embodiment. That is, an R chamfered portion 19 is formed from the first raceway 7 to the shoulder portion 17 of the outer ring member 1, the shoulder portion 18 is included from the R chamfered portion 19 to the second raceway 8, and the inner peripheral surface is on the axis of the inner ring member 4. The flat surface 20 is substantially parallel. In addition, it is good also as a C chamfering part etc. instead of this R chamfering part 19, and should just be a chamfering part. The inner ring shape of the outer ring member 1 can be easily processed because a chamfered portion may be added to the conventional structure.
[0011]
Furthermore, FIG. 3 is another embodiment. An inner peripheral surface between the first track 7 and the second track 8 of the outer ring member 1 is a flat surface 21 having a large diameter D2 substantially parallel to the axis of the inner ring member 4 formed on the shoulder 17 connected to the first track 7. The flat surface 22 having a small diameter D1 substantially parallel to the axis of the inner ring member 4 formed on the shoulder 18 connected to the second track 8 and the inclined surface 23 connecting the two flat surfaces 21 and 22 are formed. That is, there is a relationship of D2> D1. Ri due to this configuration, it becomes easy to supply cooling water at the time of quenching.
[0012]
In each of the embodiments, the shoulder inner diameter of the first track is increased, but as described in the prior art, there is no problem in performance because the design has a margin.
[0013]
【The invention's effect】
In the present invention, a chamfered portion is formed at the edge portion from the first track to the shoulder, or the portion connected to the first track has a larger diameter than the portion connected to the second track. Therefore, since the protrusion amount of the edge portion from the first track to the shoulder portion is reduced as compared with the conventional case, heat is less likely to concentrate on the edge portion during quenching, and deterioration of the structure can be prevented.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of an axle bearing device according to an embodiment of the present invention.
FIG. 2 is an enlarged view of a main part of FIG.
FIG. 3 is a cross-sectional view of an axle bearing device according to another embodiment of the present invention.
FIG. 4 is a cross-sectional view of a conventional axle bearing device.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Outer ring member 4 Inner ring member 4a Shaft end part 4b Opposite shaft end part 5 Rolling element 6 Rolling element 7 First track 8 Second track

Claims (2)

負荷荷重の大きいインナー側の内周面に第一軌道７が形成され、負荷荷重の小さいアウター側の内周面に上記第一軌道７と最外径が同じ第二軌道８が形成された一体形の外輪部材１と、外輪部材１の上記二列の軌道７，８に配装された転動体５，６を介して相対回転可能に上記外輪部材１内に配置された内輪部材４と、上記外輪部材１の第一軌道７にほぼ対応する外輪部材１外周面に車体側に固定される径方向外方フランジ１１が形成され、上記第二軌道８よりも上記第一軌道７がより強く高周波焼入れされる車軸用軸受装置において、上記外輪部材１の第一軌道７から肩部１７にかけてのエッジ部に面取り部１９が形成され、上記外輪部材１の第ニ軌道８から肩部１８にかけてのエッジ部には面取り部が形成されていないことを特徴とする車軸用軸受装置。First raceway 7 is formed on the inner peripheral surface of the large inner side of the applied load, integral outermost diameter to the inner peripheral surface and the first trajectory 7 of smaller outer side load load is formed the same second track 8 an outer ring member 1 in the form, the inner ring member 4 arranged rotatable relative to the outer ring member 1 through the rolling elements 5 and 6 which are HaiSo the track 7 and 8 of the two rows of outer ring member 1, the outer ring member 1 radially outward flange 11 which is fixed to the vehicle body on an outer peripheral surface substantially corresponding to the first track 7 of the outer ring member 1 is formed, the said first trajectory 7 than the second track 8 is stronger in an axle bearing apparatus to be induction hardened, the outer ring cut edge 19 from the first track 7 to the edge portion of the over the shoulder 17 of the member 1 is formed, over the shoulder 18 from the second raceway 8 of the outer ring member 1 wherein the non-chamfered portion formed at an edge portion Axial bearing device. 負荷荷重の大きいインナー側の内周面に第一軌道７が形成され、負荷荷重の小さいアウター側の内周面に上記第一軌道７と最外径が同じ第二軌道８が形成された一体形の外輪部材１と、外輪部材１の上記二列の軌道７，８に配装された転動体５，６を介して相対回転可能に上記外輪部材１内に配置された内輪部材４と、上記外輪部材１の第一軌道７にほぼ対応する外輪部材１外周面に車体側に固定される径方向外方フランジ１１が形成され、上記第二軌道８よりも上記第一軌道７がより強く高周波焼入れされる車軸用軸受装置において、上記外輪部材１の第一軌道７と第二軌道８の間の内周面が、第一軌道７に連なり内輪部材４の軸線に平行な大径の平坦面２１と、第二軌道８に連なり内輪部材４の軸線に平行な小径の平坦面２２と、上記大径の平坦面２１と上記小径の平坦面２２との間で両平坦面２１，２２を結合する結合面２３とから構成され、第一軌道７の最外径と上記大径の平坦面２１の内径Ｄ２との差が、第二軌道８の最外径と上記小径の平坦面２２の内径Ｄ１との差よりも小さく設定されていることを特徴とする車軸用軸受装置。First raceway 7 is formed on the inner peripheral surface of the large inner side of the applied load, integral outermost diameter to the inner peripheral surface and the first trajectory 7 of smaller outer side load load is formed the same second track 8 an outer ring member 1 in the form, the inner ring member 4 arranged rotatable relative to the outer ring member 1 through the rolling elements 5 and 6 which are HaiSo the track 7 and 8 of the two rows of outer ring member 1, the outer ring member 1 radially outward flange 11 which is fixed to the vehicle body on an outer peripheral surface substantially corresponding to the first track 7 of the outer ring member 1 is formed, the said first trajectory 7 than the second track 8 is stronger in an axle bearing apparatus to be induction hardened, the inner circumferential surface between the first track 7 of the upper Kigairin member 1 and the second track 8, a large-diameter parallel to the axis of the inner ring member 4 continues into the first track 7 a flat surface 21, a second raceway 8 flat surface 22 of the parallel small diameter to the axis of the inner ring member 4 continues into, the large It consists coupling surface 23 for coupling the two flat surfaces 21, 22 between the flat surface 21 and the smaller diameter of the flat surface 22 of the outermost and inner diameters of the flat surface 21 of the large diameter of the first raceway 7 The axle bearing device, wherein the difference from D2 is set smaller than the difference between the outermost diameter of the second track 8 and the inner diameter D1 of the flat surface 22 having the small diameter.
JP04873099A 1999-01-19 1999-01-19 Axle bearing device Expired - Fee Related JP3821979B2 (en)

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JP3821979B2 true JP3821979B2 (en) 2006-09-13

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JP5340866B2 (en) * 2009-09-17 2013-11-13 Ｎｔｎ株式会社 Wheel bearing device

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
JPS576125A (en) * 1980-06-13 1982-01-13 Nachi Fujikoshi Corp Flanged using bearing and is assembly method
JPS5746123U (en) * 1980-08-29 1982-03-13
JPS58173502U (en) * 1982-05-18 1983-11-19 株式会社不二越 Unit bearings for automobile wheels
NL8403209A (en) * 1984-10-22 1986-05-16 Skf Ind Trading & Dev ROLLER BEARING CONSTRUCTION.
JPH0830497B2 (en) * 1987-07-24 1996-03-27 光洋精工株式会社 Double-row angular contact ball bearing
JPH01190586A (en) * 1988-01-27 1989-07-31 Koyo Seiko Co Ltd Bearing device for vehicle
JPH0396717A (en) * 1989-09-11 1991-04-22 Koyo Seiko Co Ltd Radial ball bearing
JP3690821B2 (en) * 1993-12-15 2005-08-31 日本精工株式会社 Double row angular contact ball bearings for wheels
JP3932630B2 (en) * 1997-09-16 2007-06-20 日本精工株式会社 Rolling bearing unit for wheels

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