JP2007168740A - Wheel supporting bearing unit - Google Patents

Wheel supporting bearing unit Download PDF

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JP2007168740A
JP2007168740A JP2005372864A JP2005372864A JP2007168740A JP 2007168740 A JP2007168740 A JP 2007168740A JP 2005372864 A JP2005372864 A JP 2005372864A JP 2005372864 A JP2005372864 A JP 2005372864A JP 2007168740 A JP2007168740 A JP 2007168740A
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Prior art keywords
ring
peripheral surface
inner ring
outer end
flange
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Japanese (ja)
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Taketoshi Chibu
剛敏 千布
Toru Takehara
徹 竹原
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NSK Ltd
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NSK Ltd
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Priority to JP2005372864A priority Critical patent/JP2007168740A/en
Publication of JP2007168740A publication Critical patent/JP2007168740A/en
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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
    • F16C33/583—Details of specific parts of races
    • 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
    • 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
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To realize structure capable of improving the rigidity of a base part of a mounting flange 9a without increasing axial dimension of a wheel supporting bearing unit. <P>SOLUTION: In the outer peripheral surface of a hub 4a, the outer diameter D of a stage difference surface 12a formed between the inside surface of the mounting flange 9a and a cylindrical surface part 10, on which inner rings 2a and 2b are externally fitted, is formed larger than the outer diameter d of an outside flange part 15 of the one inner ring 2a existing outside. A combination seal ring 19a to be provided between the outside flange 15 and the inner peripheral surface of the outer ring 1 in an outer end thereof is provided so that an outside surface of an outside circular ring part 23 of a slinger 20 is not projected from the outer end surface of the one inner ring 2a. The described problem can be thereby solved. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、懸架装置に対して車輪を回転自在に支持する為に利用する車輪支持用軸受ユニットの改良に関する。   The present invention relates to an improvement of a bearing unit for supporting a wheel which is used for rotatably supporting a wheel with respect to a suspension device.

自動車の車輪を懸架装置に対して回転自在に支持する為に従来から、車輪支持用軸受ユニットが使用されている。図３は、この車輪支持用軸受ユニットの従来構造の１例として、特許文献１に記載された、駆動輪（ＦＦ車の前輪、ＦＲ車及びＲＲ車の後輪、４ＷＤ車の全車輪）用のものを示している。この車輪支持用軸受ユニットは、外輪１と、１対の内輪２ａ、２ｂと、それぞれが転動体である複数個の円すいころ３、３と、軸部材であるハブ４とを備える。   2. Description of the Related Art Conventionally, a wheel support bearing unit has been used to rotatably support a vehicle wheel with respect to a suspension device. FIG. 3 shows an example of the conventional structure of this wheel support bearing unit, which is described in Patent Document 1, for driving wheels (front wheels of FF vehicles, rear wheels of FR and RR vehicles, all wheels of 4WD vehicles). Shows things. The wheel support bearing unit includes an outer ring 1, a pair of inner rings 2a and 2b, a plurality of tapered rollers 3 and 3 each of which is a rolling element, and a hub 4 which is a shaft member.

このうちの外輪１は、内周面にそれぞれが円すい面状である第一、第二の外輪軌道５ａ、５ｂを、外周面に結合フランジ６を、それぞれ形成している。上記第一、第二の各外輪軌道５ａ、５ｂの傾斜方向は、互いに逆にしている。又、上記１対の内輪２ａ、２ｂのうち、外側（軸方向に関して外とは、自動車への組み付け状態で車両の幅方向外側を言い、各図の左側。反対に、車両の幅方向中央側となる、各図の右側を、軸方向に関して内と言う。本明細書及び特許請求の範囲の全体で同じ。）に存在する一方の内輪２ａは、外周面に円すい面状の第一の内輪軌道７ａを、内側に存在する他方の内輪２ｂは、外周面に円すい面状の第二の内輪軌道７ｂを、それぞれ形成している。この様な両内輪２ａ、２ｂは、それぞれの小径側端面同士を互いに付き合わせた状態で、上記外輪１の径方向内側に、この外輪１と同心に配置している。   Of these, the outer ring 1 has first and second outer ring raceways 5a and 5b each having a conical shape on the inner peripheral surface, and a coupling flange 6 on the outer peripheral surface. The inclination directions of the first and second outer ring raceways 5a and 5b are opposite to each other. Of the pair of inner rings 2a and 2b, the outside (the outside in the axial direction means the outside in the width direction of the vehicle in the assembled state to the automobile, the left side of each figure. The right side of each figure is said to be inward with respect to the axial direction.This is the same throughout the present specification and claims.) One inner ring 2a is a first inner ring having a conical surface on the outer peripheral surface. The other inner ring 2b existing inside the track 7a forms a conical second inner ring track 7b on the outer peripheral surface. Both the inner rings 2a and 2b are arranged concentrically with the outer ring 1 on the radially inner side of the outer ring 1 in a state where the respective end surfaces on the small diameter side are attached to each other.

又、上記各円すいころ３、３は、上記第一、第二の外輪軌道５ａ、５ｂと上記第一、第二の内輪軌道７ａ、７ｂとの間に、それぞれ複数個ずつ、保持器８、８により保持した状態で転動自在に設けている。尚、図示の例は、重量が嵩む自動車用の車輪支持用軸受ユニットである為、転動体として円すいころ３、３を使用しているが、重量が嵩まない自動車用の車輪支持用軸受ユニットの場合には、転動体として玉を使用する場合もある。   Each of the tapered rollers 3 and 3 includes a plurality of cages 8 between the first and second outer ring raceways 5a and 5b and the first and second inner ring raceways 7a and 7b. 8 is provided so that it can roll freely. The illustrated example is a wheel support bearing unit for automobiles that is heavy in weight. Therefore, although the tapered rollers 3 and 3 are used as rolling elements, the wheel support bearing unit for automobiles that does not increase in weight. In this case, balls may be used as rolling elements.

又、上記ハブ４は、外周面の外端寄り部分に、車輪を支持固定する為の取付フランジ９を、同じく中央部乃至内端部に円筒面部１０を、中心部にスプライン孔１１を、それぞれ形成している。そして、このうちの円筒面部１０に上記両内輪２ａ、２ｂを、それぞれの大径側端部外周面に形成した、外側、内側両鍔部１５、１６を互いに反対側に位置させて、それぞれ締め代を持たせた状態で（圧入した状態で）外嵌支持している。又、この状態で、上記一方の内輪２ａの大径側端面を、上記ハブ４の外周面で上記取付フランジ９の内側面と上記円筒面部１０との間に形成した段差面１２に突き当てている。又、上記ハブ４の内端部で他方の内輪２ｂの大径側端面よりも軸方向内方に突出した部分に円筒部１３を設け、この円筒部１３を径方向外方に塑性変形させる事により、かしめ部１４を形成している。そして、このかしめ部１４により、上記他方の内輪２ｂの大径側端面（内端面）を、上記段差面１２に向け抑え付けている。そして、この様に抑え付ける事により、両内輪２ａ、２ｂに、軸方向に関して互いに近づき合う方向の力を付与している。これにより、前記各円すいころ３、３に、背面組み合わせ型の接触角を付与している。   Further, the hub 4 has a mounting flange 9 for supporting and fixing the wheel at a portion near the outer end of the outer peripheral surface, a cylindrical surface portion 10 at the center or inner end portion, and a spline hole 11 at the center portion. Forming. Then, the inner ring 2a, 2b is formed on the cylindrical surface portion 10 on the outer peripheral surface of each large-diameter side end portion, and the outer and inner flange portions 15, 16 are positioned on the opposite sides, and tightened. The outer fitting is supported with the allowance (in the press-fitted state). Further, in this state, the large-diameter side end surface of the one inner ring 2 a is abutted against the step surface 12 formed between the inner surface of the mounting flange 9 and the cylindrical surface portion 10 on the outer peripheral surface of the hub 4. Yes. Further, a cylindrical portion 13 is provided at a portion of the inner end portion of the hub 4 that protrudes inward in the axial direction from the end surface on the larger diameter side of the other inner ring 2b, and the cylindrical portion 13 is plastically deformed radially outward. Thus, the caulking portion 14 is formed. The caulking portion 14 holds the large-diameter side end surface (inner end surface) of the other inner ring 2 b toward the step surface 12. And by suppressing in this way, the force of the direction which mutually approaches in the axial direction is provided to both inner ring | wheels 2a and 2b. Thereby, a contact angle of a back combination type is given to each of the tapered rollers 3 and 3.

又、上記外輪１の外端部内周面と、上記一方の内輪２ａの外端部外周面で上記第一の内輪軌道７ａから外れた部分に形成した外側鍔部１５との間、及び、上記外輪１の内端部内周面と、上記他方の内輪２ｂの内端部外周面で上記第二の内輪軌道７ｂから外れた部分に形成した内側鍔部１６との間に、それぞれ密封装置１７ａ、１７ｂを設けている。そして、上記外輪１の内周面と上記両内輪２ａ、２ｂの外周面との間で、前記各円すいころ３、３が存在する内部空間１８の両端開口部を塞いでいる。これにより、この内部空間１８内に封入したグリース等の潤滑剤が外部に漏れる事を防止すると共に、外部からこの内部空間１８内に塵芥等の異物が浸入する事を防止している。   Further, between the outer peripheral surface of the outer end portion of the outer ring 1 and the outer flange portion 15 formed on the outer peripheral portion of the outer end portion of the one inner ring 2a at a portion deviated from the first inner ring raceway 7a, and A sealing device 17a, between an inner peripheral surface of the inner end portion of the outer ring 1 and an inner flange portion 16 formed on a portion of the inner end portion outer peripheral surface of the other inner ring 2b that is separated from the second inner ring raceway 7b, 17b is provided. And between the inner peripheral surface of the said outer ring | wheel 1 and the outer peripheral surface of both said inner ring | wheels 2a and 2b, the both-ends opening part of the internal space 18 in which each said tapered roller 3 and 3 exists is block | closed. Thereby, the lubricant such as grease sealed in the internal space 18 is prevented from leaking to the outside, and foreign substances such as dust are prevented from entering the internal space 18 from the outside.

上述の様な車輪支持用軸受ユニットを自動車に組み付ける場合には、図示しない等速ジョイントを構成するスプライン軸を、前記スプライン孔１１に挿入する。又、前記結合フランジ６を、図示しない懸架装置を構成するナックルに結合固定すると共に、前記取付フランジ９に、図示しない車輪及びブレーキロータ等を支持固定する。これにより、これら車輪及びブレーキロータ等を上記懸架装置に対して支持すると共に、これら車輪及びブレーキロータ等を回転駆動自在とする。尚、図示の例では、上記外輪１の外周面に上記結合フランジ６を設けているが、この外輪１の外周面を単なる円筒面とした構造も、従来から存在する。この様な構造の場合、外周面を単なる円筒面とした外輪１は、懸架装置を構成するナックルに設けた円形の支持孔の内側に、軸方向の位置決めを図った状態で内嵌支持する。   When the wheel support bearing unit as described above is assembled to an automobile, a spline shaft constituting a constant velocity joint (not shown) is inserted into the spline hole 11. The coupling flange 6 is coupled and fixed to a knuckle that constitutes a suspension device (not shown), and wheels and brake rotors (not shown) are supported and fixed to the mounting flange 9. As a result, the wheels, the brake rotor, and the like are supported with respect to the suspension device, and the wheels, the brake rotor, and the like are rotatable. In the illustrated example, the coupling flange 6 is provided on the outer peripheral surface of the outer ring 1. However, there is a conventional structure in which the outer peripheral surface of the outer ring 1 is a simple cylindrical surface. In the case of such a structure, the outer ring 1 whose outer peripheral surface is a simple cylindrical surface is fitted and supported inside the circular support hole provided in the knuckle constituting the suspension device in a state where the axial positioning is achieved.

上述した様に、車輪支持用軸受ユニットは、取付フランジ９に車輪を支持する。この為、走行時に、この取付フランジ９がこの車輪から荷重を受ける。図３に示した従来構造の場合、上記取付フランジ９の内側面と円筒面部１０との間に存在する段差面１２の外径は、外側に存在する一方の内輪２ａの外側鍔部１５の外径と同じ大きさである。この為、従来構造の場合、上記取付フランジ９の基端部の厚さが小さく、この基端部の剛性がそれ程高くはなかった。この様に、取付フランジ９の基端部の剛性がそれ程高くないと、走行時に車輪から受ける荷重により、図３のイ〜ハ部分に、特に大きな応力が作用する。車輪支持用軸受ユニットの耐久性の向上等を図る為には、これらイ〜ハ部分に生じる応力を小さくする事が有効である。この為に、上記取付フランジ９の基端部の軸方向の厚さを大きくする事により、この基端部の剛性を高くして、上記イ〜ハ部分の応力を低減する事が考えられる。但し、この場合には、車輪支持用軸受ユニットの軸方向寸法並びに重量が嵩む。この車輪支持用軸受ユニットは、狭い空間に設置する場合があり、又、所謂ばね下荷重となって、少しの重量増大も、走行性態に悪影響を及ぼす為、軸方向寸法や重量が嵩む事は好ましくない。   As described above, the wheel support bearing unit supports the wheel on the mounting flange 9. For this reason, the mounting flange 9 receives a load from the wheel during traveling. In the case of the conventional structure shown in FIG. 3, the outer diameter of the step surface 12 existing between the inner surface of the mounting flange 9 and the cylindrical surface portion 10 is the outer diameter of the outer flange portion 15 of one inner ring 2a existing on the outer side. It is the same size as the diameter. For this reason, in the conventional structure, the thickness of the base end portion of the mounting flange 9 is small, and the rigidity of the base end portion is not so high. In this way, if the rigidity of the base end portion of the mounting flange 9 is not so high, a particularly large stress acts on portions A to C in FIG. 3 due to the load received from the wheel during traveling. In order to improve the durability of the wheel support bearing unit, it is effective to reduce the stress generated in these parts a to c. For this reason, it is conceivable to increase the rigidity of the base end part by increasing the axial thickness of the base end part of the mounting flange 9 and to reduce the stress in the parts A to C. However, in this case, the axial dimension and weight of the wheel supporting bearing unit increase. This wheel support bearing unit may be installed in a narrow space, and becomes a so-called unsprung load, and even a slight increase in weight adversely affects the running condition, increasing the axial dimension and weight. Is not preferred.

特開２００４−２５７５５６号公報JP 2004-257556 A

本発明の車輪支持用軸受ユニットは、上述の様な事情に鑑み、車輪支持用軸受ユニットの軸方向寸法を大きくする事なく、又、重量増大を僅少に抑えつつ、取付フランジの基端部の剛性を高くできる構造を実現すべく発明したものである。   In view of the circumstances as described above, the wheel support bearing unit of the present invention is not required to increase the axial dimension of the wheel support bearing unit, and while suppressing the increase in weight slightly, It was invented to realize a structure capable of increasing the rigidity.

本発明の車輪支持用軸受ユニットは、外輪と、１対の内輪と、転動体と、軸部材とを備える。
このうちの外輪は、内周面に複列の外輪軌道を形成している。
又、上記両内輪は、それぞれの外周面に単列の内輪軌道を形成している。
又、上記転動体は、上記各外輪軌道と各内輪軌道との間にそれぞれ複数個ずつ転動自在に設けている。
又、上記軸部材は、外端寄り外周面に車輪を固定する為の取付フランジを、中間部乃至内端部外周面に上記両内輪を締め代を持たせて外嵌する円筒面部を、それぞれ形成している。
そして、上記１対の内輪のうちの外側に存在する一方の内輪を上記円筒面部に外嵌した状態で、この一方の内輪の外端面を、この軸部材の外周面で、上記取付フランジの内側面と上記円筒面部との間に形成した段差面に突き当てている。
特に、本発明の車輪支持用軸受ユニットに於いては、上記段差面の外径を、上記一方の内輪の外端部の外径よりも大きくしている。 The wheel support bearing unit of the present invention includes an outer ring, a pair of inner rings, a rolling element, and a shaft member.
Among these, the outer ring forms a double row outer ring raceway on the inner peripheral surface.
The inner rings form a single-row inner ring raceway on their outer peripheral surfaces.
A plurality of rolling elements are provided between the outer ring raceways and the inner ring raceways so as to be freely rollable.
The shaft member includes a mounting flange for fixing the wheel to the outer peripheral surface near the outer end, and a cylindrical surface portion for externally fitting the inner ring to the outer peripheral surface of the intermediate portion or the inner end portion with a tightening margin. Forming.
Then, with one inner ring existing outside of the pair of inner rings fitted on the cylindrical surface portion, the outer end surface of the one inner ring is connected to the inner peripheral surface of the mounting flange with the outer peripheral surface of the shaft member. It abuts against a step surface formed between the side surface and the cylindrical surface portion.
In particular, in the wheel support bearing unit of the present invention, the outer diameter of the stepped surface is made larger than the outer diameter of the outer end portion of the one inner ring.

又、請求項２に記載した様に、本発明を、外輪の外端部内周面と、一方の内輪の外端部外周面で内輪軌道から外れた部分に形成した鍔部との間に、スリンガとシールリングとを組み合わせて成る組み合わせシールリングを設けた構造に適用する場合がある。
このうちのスリンガは、一方の内輪の鍔部に外嵌固定する内径側円筒部と、この内径側円筒部の外端縁から径方向外方に折れ曲った外側円輪部とから成る。
又、上記シールリングは、外輪の外端部内周面に内嵌固定する外径側円筒部とこの外径側円筒部の内端縁から径方向内方に折れ曲った内側円輪部とから成る芯金と、上記外径側円筒部の内周面乃至上記内側円輪部の外側面に添着され、内周縁部に形成したシールリップを上記スリンガの一部に摺接させる、弾性材とから成る。
そして、請求項２に記載した発明の場合には、上記組み合わせシールリングを、上記スリンガの外側円輪部の外側面が上記一方の内輪の外端面よりも外方に突出しない様に、設置する。 In addition, as described in claim 2, the present invention is provided between the inner peripheral surface of the outer end portion of the outer ring and the flange portion formed on the outer end outer peripheral surface of one of the inner rings at a portion off the inner ring raceway. In some cases, the present invention is applied to a structure provided with a combination seal ring formed by combining a slinger and a seal ring.
Of these, the slinger is composed of an inner diameter side cylindrical portion that is fitted and fixed to the flange portion of one inner ring, and an outer ring portion that is bent radially outward from the outer end edge of the inner diameter side cylindrical portion.
The seal ring includes an outer diameter side cylindrical portion that is fitted and fixed to the inner peripheral surface of the outer end portion of the outer ring, and an inner ring portion that is bent radially inward from the inner end edge of the outer diameter side cylindrical portion. And an elastic material attached to an inner peripheral surface of the outer diameter side cylindrical portion or an outer side surface of the inner annular ring portion, and a sliding lip formed on the inner peripheral edge portion in sliding contact with a part of the slinger. Consists of.
In the case of the invention described in claim 2, the combination seal ring is installed so that the outer surface of the outer ring portion of the slinger does not protrude outward from the outer end surface of the one inner ring. .

上述の様に構成する本発明の車輪支持用軸受ユニットの場合には、車輪支持用軸受ユニットの軸方向寸法を大きくする事なく、又、重量増大を僅少に抑えつつ、取付フランジの基端部の剛性を高くできる。即ち、この取付フランジの内側面と円筒面部との間に存在する段差面の外径寸法を大きくする事により、この取付フランジの基端部の肉厚を大きくして、この基端部の剛性を高くできる。又、上記段差面の外径寸法を大きくしているのみである為、上記車輪支持用軸受ユニットの軸方向寸法が大きくなる事はないし、重量増大も僅少に抑えられる。   In the case of the wheel support bearing unit of the present invention configured as described above, the base end portion of the mounting flange without increasing the axial dimension of the wheel support bearing unit and suppressing a slight increase in weight. The rigidity of can be increased. That is, by increasing the outer diameter of the step surface existing between the inner surface of the mounting flange and the cylindrical surface portion, the thickness of the base end portion of the mounting flange is increased, and the rigidity of the base end portion is increased. Can be high. Further, since only the outer diameter of the stepped surface is increased, the axial dimension of the wheel support bearing unit is not increased, and the increase in weight can be suppressed to a small extent.

又、請求項２に記載した様に、一方の内輪の外端部外周面に形成した鍔部に組み合わせシールリングを設置した場合、この一方の内輪の外端面を突き当てる段差面の外径寸法が大きくなると、上記鍔部に外嵌する上記組み合わせシールリングのスリンガの外側円輪部が、上記段差面と干渉する可能性がある。この為、この外側円輪部の外側面が、上記一方の内輪の外端面よりも外方に突出しない様に、上記組み合わせシールリングの設置位置を規制して、上記外側円輪部と上記段差面とが干渉しない様にする。   In addition, as described in claim 2, when a combination seal ring is installed on the flange formed on the outer peripheral surface of the outer end of one inner ring, the outer diameter of the step surface that abuts the outer end surface of the one inner ring. When becomes larger, there is a possibility that the outer ring portion of the slinger of the combined seal ring that fits around the flange portion interferes with the step surface. For this reason, the installation position of the combination seal ring is restricted so that the outer surface of the outer ring portion does not protrude outward from the outer end surface of the one inner ring, and the step difference between the outer ring portion and the step Avoid interference with the surface.

図１は、本発明の実施の形態の１例を示している。尚、本発明の特徴は、車輪支持用軸受ユニットの軸方向寸法を大きくする事なく、又、重量の増大を僅少に抑えつつ、取付フランジ９ａの基端部の剛性を高くすべく、段差面１２ａの外径寸法を大きくする点にある。その他の構造及び作用は、前述の図３に記載した従来構造と同様である為、同等部分には同一符号を付して、重複する説明を省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。   FIG. 1 shows an example of an embodiment of the present invention. It should be noted that the feature of the present invention is that a stepped surface is used in order to increase the rigidity of the base end portion of the mounting flange 9a without increasing the axial dimension of the wheel support bearing unit and suppressing the increase in weight slightly. The outer diameter of 12a is increased. Since the other structure and operation are the same as those of the conventional structure described in FIG. 3, the same reference numerals are given to the equivalent parts, and the overlapping description is omitted or simplified. The explanation is centered.

本例の場合、内部空間１８の両端開口部を塞ぐ密封装置を、組み合わせシールリング１９ａ、１９ｂとしている。このうちの外端側開口部を塞ぐ組み合わせシールリング１９ａは、スリンガ２０とシールリング２１とを組み合わせて成る。このうちのスリンガ２０は、外側に存在する一方の内輪２ａの外側鍔部１５に外嵌固定する内径側円筒部２２と、この内径側円筒部２２の外端縁から径方向外方に折れ曲った外側円輪部２３とから成る。又、上記シールリング２１は、芯金２４と、弾性材２５とから成る。このうちの芯金２４は、外輪１の外端部内周面に内嵌固定する外径側円筒部２６とこの外径側円筒部２６の内端縁から径方向内方に折り曲げた内側円輪部２７とから成る。又、上記弾性材２５は、上記外径側円筒部２６の内周面乃至上記内側円輪部２７の外側面に添着されている。又、この弾性材２５の内周縁部に形成したシールリップ２８、２８を、上記スリンガ２０を構成する内径側円筒部２２の外周面及び外側円輪部２３の内側面の一部に摺接させている。尚、上記内部空間１８の内端側開口部を塞ぐ組み合わせシールリング１９ｂに就いても、上述の組み合わせシールリング１９ａと同様の構造を有する。   In the case of this example, the sealing devices that close the opening portions at both ends of the internal space 18 are combined seal rings 19a and 19b. Among these, the combination seal ring 19 a that closes the outer end side opening is formed by combining the slinger 20 and the seal ring 21. Among them, the slinger 20 is bent radially outwardly from the inner diameter side cylindrical portion 22 that is fitted and fixed to the outer flange portion 15 of one inner ring 2 a that is present on the outer side, and the outer end edge of the inner diameter side cylindrical portion 22. And an outer ring portion 23. The seal ring 21 includes a cored bar 24 and an elastic material 25. Of these, the core metal 24 includes an outer diameter side cylindrical portion 26 that is fitted and fixed to the inner peripheral surface of the outer end portion of the outer ring 1, and an inner ring that is bent radially inward from the inner end edge of the outer diameter side cylindrical portion 26. Part 27. The elastic member 25 is attached to the inner peripheral surface of the outer diameter side cylindrical portion 26 or the outer surface of the inner ring portion 27. Further, the seal lips 28, 28 formed on the inner peripheral edge of the elastic member 25 are brought into sliding contact with the outer peripheral surface of the inner diameter side cylindrical portion 22 constituting the slinger 20 and a part of the inner side surface of the outer ring portion 23. ing. Note that the combination seal ring 19b that closes the inner end side opening of the internal space 18 has the same structure as the combination seal ring 19a.

特に、本例の場合、ハブ４ａの外周面で、前記取付フランジ９ａの内側面と、１対の内輪２ａ、２ｂを外嵌する円筒面部１０との間に存在する前記段差面１２ａの外径Ｄを、上記一方の内輪２ａの外側鍔部１５の外径ｄよりも大きく（Ｄ＞ｄ）している。この為、上記取付フランジ９ａの基端部の肉厚を厚くできる。但し、この段差面１２ａの外径Ｄは、上記外輪１の外端部の内径Ｒよりも小さく（Ｄ＜Ｒ）している。そして、上記取付フランジ９ａの内側面のうち、上記段差面１２ａよりも外径側部分で外輪１の外端面と対向する部分に、この段差面１２ａよりも軸方向外方に存在する、第二の段差面２９を形成している。尚、上記ハブ４ａと上記外輪１とを組み付けた状態で、この第二の段差面２９とこの外輪１の外端面との間に隙間が存在する。この隙間の存在により、走行時等に、上記取付フランジ９ａに曲げ応力が作用する等して、上記第二の段差面２９と上記外輪１の外端面との距離が近づく場合でも、これら両面が接触する事はない。尚、上記外側鍔部１５の外径ｄに比べて、上記段差面１２ａの外径Ｄを大きくする程度（Ｄ−ｄ）は、好ましくは、上記外輪１の外端部の内径Ｒと上記外側鍔部１５の外径ｄとの差の１／３以上｛（Ｄ−ｄ）≧（Ｒ−ｄ）／３｝、より好ましくは１／２以上｛（Ｄ−ｄ）≧（Ｒ−ｄ）／２｝とする。   In particular, in the case of this example, the outer diameter of the step surface 12a existing between the inner surface of the mounting flange 9a and the cylindrical surface portion 10 on which the pair of inner rings 2a and 2b are fitted on the outer peripheral surface of the hub 4a. D is larger than the outer diameter d of the outer flange 15 of the one inner ring 2a (D> d). For this reason, the thickness of the base end portion of the mounting flange 9a can be increased. However, the outer diameter D of the stepped surface 12a is smaller than the inner diameter R of the outer end portion of the outer ring 1 (D <R). Of the inner side surface of the mounting flange 9a, a second outer side of the stepped surface 12a that is opposed to the outer end surface of the outer ring 1 on the outer diameter side portion is located outside the stepped surface 12a in the axial direction. The step surface 29 is formed. In the state where the hub 4 a and the outer ring 1 are assembled, a gap exists between the second step surface 29 and the outer end surface of the outer ring 1. Even if the distance between the second stepped surface 29 and the outer end surface of the outer ring 1 approaches due to the presence of this gap, a bending stress acts on the mounting flange 9a during traveling, etc. There is no contact. It should be noted that the degree (Dd) of increasing the outer diameter D of the stepped surface 12a relative to the outer diameter d of the outer flange 15 is preferably the inner diameter R of the outer end of the outer ring 1 and the outer diameter. 1/3 or more of the difference from the outer diameter d of the flange 15 {(D−d) ≧ (R−d) / 3}, more preferably 1/2 or more {(D−d) ≧ (R−d) / 2}.

言い換えれば、本例の場合、上記第二の段差面２９を形成する事によって、上記取付フランジ９ａの径方向中間部の肉厚も厚く（或る程度の肉厚を確保）している。但し、上述の様に、第二の段差面２９を上記段差面１２ａよりも軸方向外方に形成して、この第二の段差面２９と上記外輪１の外端面との干渉を防止している。これに対して、段差面１２ａと外輪１の外端面との軸方向に関する距離が離れている場合には、この段差面１２ａの外径Ｄを、この外輪１の外端部の内径よりも大きくする事もできる。この場合には、上述した様な第二の段差面は必要ない。又、上記取付フランジ９ａの軸方向内側面のうち、上記第二の段差面２９よりも外径側部分を、この第二の段差面２９と面一にしても良い。これにより、上記取付フランジ９ａの肉厚を全体的に厚くでき、強度確保の面から有利になる。   In other words, in the case of this example, by forming the second stepped surface 29, the thickness of the intermediate portion in the radial direction of the mounting flange 9a is increased (a certain thickness is ensured). However, as described above, the second step surface 29 is formed axially outward from the step surface 12a to prevent interference between the second step surface 29 and the outer end surface of the outer ring 1. Yes. On the other hand, when the distance in the axial direction between the step surface 12a and the outer end surface of the outer ring 1 is large, the outer diameter D of the step surface 12a is larger than the inner diameter of the outer end portion of the outer ring 1. You can also do it. In this case, the second step surface as described above is not necessary. Further, the outer diameter side portion of the mounting flange 9 a in the axial direction with respect to the second stepped surface 29 may be flush with the second stepped surface 29. Thereby, the thickness of the mounting flange 9a can be increased as a whole, which is advantageous in terms of securing the strength.

又、本例の場合、上記一方の内輪２ａの外側鍔部１５と上記外輪１の外端部内周面との間に設置する、前記組み合わせシールリング１９ａを、上記一方の内輪２ａの外端面に対して内方に設置している。この為、この組み合わせシールリング１９ａを構成する、前記スリンガ２０の外側円輪部２３の外側面が、上記一方の内輪２ａの外端面よりも内方に存在する。尚、上記外側鍔部１５の軸方向寸法は、必ずしも図１に示した程に大きくする必要はない。要は、外側の円すいころ列を保持する保持器８と干渉しない程度に、上記組み合わせシールリング１９ａを、上記一方の内輪２ａの外端面よりも僅かでも内方に設置できれば良い。従って、上記組み合わせシールリング１９ａを、この外端面に対して内方に設置する為にだけ、上記一方の内輪２ａの軸方向寸法、延いては、車輪支持用軸受ユニットの軸方向寸法を大きくする必要はない。   In the case of this example, the combined seal ring 19a installed between the outer flange 15 of the one inner ring 2a and the inner peripheral surface of the outer end of the outer ring 1 is provided on the outer end surface of the one inner ring 2a. On the other hand, it is installed inward. For this reason, the outer side surface of the outer ring portion 23 of the slinger 20 constituting the combined seal ring 19a is present inward from the outer end surface of the one inner ring 2a. Note that the axial dimension of the outer flange 15 need not necessarily be as large as shown in FIG. In short, it is only necessary that the combined seal ring 19a can be installed slightly inward from the outer end surface of the one inner ring 2a to the extent that it does not interfere with the cage 8 that holds the outer tapered roller row. Accordingly, only in order to install the combined seal ring 19a inward with respect to the outer end surface, the axial dimension of the one inner ring 2a, and hence the axial dimension of the wheel support bearing unit, is increased. There is no need.

上述の様に構成する本例の車輪支持用軸受ユニットの場合には、車輪支持用軸受ユニットの軸方向寸法を大きくする事なく、又、重量の増大を僅少に抑えつつ、取付フランジ９ａの基端部の剛性を高くできる。即ち、この取付フランジ９ａの内側面と、前記円筒面部１０との間に存在する段差面１２ａの外径寸法を大きくする事により、上記取付フランジ９ａの基端部の肉厚を大きくできる。又、本例の場合、上記段差面１２ａの外径側に第二の段差面２９を形成して、上記取付フランジ９ａの径方向中間部の肉厚も厚くしている。この為、この取付フランジ９ａの基端部乃至中間部の肉厚を十分に大きくして、この取付フランジ９ａの基端部の剛性を高くできる。この結果、この基端部のうちの、特に、図１のイ〜ハ部分に作用する応力を低減できる。又、上記段差面１２ａの外径寸法を大きくしているのみである為、上記車輪支持用軸受ユニットの軸方向寸法が大きくなる事はないし、重量の増大も僅少に抑えられる。   In the case of the wheel support bearing unit of the present example configured as described above, the base of the mounting flange 9a is not increased without increasing the axial dimension of the wheel support bearing unit and while suppressing a slight increase in weight. The rigidity of the end can be increased. That is, by increasing the outer diameter of the step surface 12a existing between the inner side surface of the mounting flange 9a and the cylindrical surface portion 10, the thickness of the base end portion of the mounting flange 9a can be increased. In the case of this example, the second step surface 29 is formed on the outer diameter side of the step surface 12a, and the thickness of the intermediate portion in the radial direction of the mounting flange 9a is also increased. For this reason, the thickness of the base end part to the intermediate part of the mounting flange 9a can be made sufficiently large to increase the rigidity of the base end part of the mounting flange 9a. As a result, it is possible to reduce the stress acting on the portions A to C in FIG. Further, since only the outer diameter dimension of the stepped surface 12a is increased, the axial dimension of the wheel support bearing unit is not increased, and the increase in weight is suppressed to a slight extent.

又、本例の様に、内部空間１８の外端側開口部を塞ぐ密封装置として、組み合わせシールリング１９ａを使用した場合でも、この組み合わせシールリング１９ａを構成するスリンガ２０の外側円輪部２３が、上記段差面１２ａと干渉する事はない。即ち、前記一方の内輪２ａの外端面を突き当てるこの段差面１２ａの外径寸法が大きくなると、この内輪２ａの外端部外周面に形成した外側鍔部１５に外嵌する上記スリンガ２０の外側円輪部２３が、上記段差面１２ａと干渉する可能性がある。   Further, as in this example, even when the combined seal ring 19a is used as a sealing device for closing the outer end side opening of the internal space 18, the outer ring portion 23 of the slinger 20 constituting the combined seal ring 19a is There is no interference with the step surface 12a. That is, when the outer diameter of the step surface 12a that abuts the outer end surface of the one inner ring 2a is increased, the outer side of the slinger 20 that is externally fitted to the outer flange 15 formed on the outer peripheral surface of the outer end of the inner ring 2a. There is a possibility that the circular ring portion 23 interferes with the step surface 12a.

例えば、上記スリンガ２０の外側面が上記一方の内輪２ａの外端面よりも外方に突出した場合、この一方の内輪２ａを上記ハブ４ａの円筒面部１０に外嵌して、この一方の内輪２ａの外端面を上記段差面１２ａに突き当てる際に、上記スリンガ２０がこの段差面１２ａにより軸方向内方に押される。この結果、前記弾性材２５のシールリップ２８、２８と上記スリンガ２０との摺接部の当接圧が変化したり、これら各シールリップ２８、２８のうちの何れかのシールリップ２８がめくれる等して、上記組み合わせシールリング１９ａに不具合が生じる可能性がある。この為、本例の場合、上記スリンガ２０の外側円輪部２３の外側面が、上記一方の内輪２ａの外端面よりも外方に突出しない様に、上記組み合わせシールリング１９ａの設置位置を規制して、上記外側円輪部２３と上記段差面１２ａとが干渉しない様にしている。   For example, when the outer surface of the slinger 20 protrudes outward from the outer end surface of the one inner ring 2a, the one inner ring 2a is externally fitted to the cylindrical surface portion 10 of the hub 4a, and the one inner ring 2a The aforesaid slinger 20 is pushed inward in the axial direction by the step surface 12a. As a result, the contact pressure of the sliding contact portion between the seal lips 28, 28 of the elastic material 25 and the slinger 20 changes, or any one of the seal lips 28, 28 is turned over. As a result, the combination seal ring 19a may be defective. For this reason, in this example, the installation position of the combination seal ring 19a is regulated so that the outer surface of the outer ring portion 23 of the slinger 20 does not protrude outward from the outer end surface of the one inner ring 2a. Thus, the outer ring portion 23 and the step surface 12a are prevented from interfering with each other.

但し、上記組み合わせシールリング１９ａの設置位置は、上記スリンガ２０の外側円輪部２３の外側面の軸方向位置が、上記一方の内輪２ａの外端面と同じとなっても良い。即ち、上記スリンガ２０は、上記一方の内輪２ａに外嵌固定されている為、この一方の内輪２ａを外嵌したハブ４ａと共に回転する。この為、上記スリンガ２０の外側円輪部２３がこのハブ４ａの外周面の一部である上記段差面１２ａと接触しても問題ない。従って、上記外側円輪部２３の外側面の軸方向位置を、上記一方の内輪２ａの外端面と同じにできる。但し、走行時に、車輪から作用する荷重により取付フランジ９ａに曲げ応力が作用した場合、上記外側円輪部２３の外側面と上記段差面１２ａとが接触していると、この外側円輪部２３がこの段差面１２ａに押される可能性がある。この為、本例の様に、この外側円輪部２３の外側面を上記一方の内輪２ａの外端面よりも内方に位置させて、この外側円輪部２３の外側面と上記段差面１２ａとの間に隙間を存在させる事が好ましい。   However, as for the installation position of the combination seal ring 19a, the axial position of the outer surface of the outer ring portion 23 of the slinger 20 may be the same as the outer end surface of the one inner ring 2a. That is, since the slinger 20 is externally fitted and fixed to the one inner ring 2a, the slinger 20 rotates together with the hub 4a that externally fits the one inner ring 2a. Therefore, there is no problem even if the outer ring portion 23 of the slinger 20 contacts the step surface 12a which is a part of the outer peripheral surface of the hub 4a. Accordingly, the axial position of the outer surface of the outer ring portion 23 can be made the same as the outer end surface of the one inner ring 2a. However, when a bending stress is applied to the mounting flange 9a due to a load applied from the wheel during traveling, if the outer surface of the outer ring portion 23 and the stepped surface 12a are in contact with each other, the outer ring portion 23 is removed. May be pushed by the step surface 12a. Therefore, as in this example, the outer surface of the outer ring portion 23 is positioned inward of the outer end surface of the one inner ring 2a, and the step surface 12a and the outer surface of the outer ring portion 23 are located. It is preferable to have a gap between the two.

上述した実施の形態の１例では、車輪支持用軸受ユニットとして、駆動輪用のものに就いて説明したが、本発明は、従動輪（ＦＦ車の後輪、ＦＲ車及びＲＲ車の前輪）用の車輪支持用軸受ユニットにも適用できる。又、上述の実施の形態の１例では、転動体として円すいころを使用したものに就いて説明したが、転動体は玉であっても良い。更に、図１に示した構造で、内部空間１８の開口端部を塞ぐ密封装置の構造として、図示の組み合わせシールリング１９ａ以外に、例えば、図２（Ａ）、（Ｂ）に示す様な密封装置１７ｃ、１７ｄを使用しても良い。このうちの（Ａ）の構造の場合、芯金２４ａを外輪１の外端部内周面に内嵌固定し、弾性材２５ａの内周縁部に形成したシールリップ２８ａ、２８ａを、内輪２ａの外側鍔部１５（又は内輪２ｂの内側鍔部１６）に摺接させる。外側鍔部１５に摺接させる場合には、軸方向外方のシールリップ２８ａが段差面１２ａと干渉しない様にする。又、（Ｂ）の構造の場合、芯金２４ｂを外輪１の外端部内周面に内嵌固定し、スリンガ２０ａを内輪２ａの外側鍔部１５（又は内輪２ｂの内側鍔部１６）に外嵌固定する。そして、上記芯金２４ｂの内周縁部に設けた弾性材２５ｂのシールリップ２８ｂを、上記スリンガ２０ａの内径側円筒部２２の外周面に、このスリンガ２０ａの外周縁部に設けた弾性材２５ｃのシールリップ２８ｃ、２８ｃを、上記芯金２４ｂの外径側円筒部２６の内周面及び内側円輪部２７の外側面に、それぞれ摺接させる。上記スリンガ２０ａを外側鍔部１５に外嵌固定する場合には、このスリンガ２０ａの外側円輪部２３が段差面１２ａと干渉しない様にする。   In one example of the embodiment described above, the wheel support bearing unit has been described for the drive wheel. However, the present invention is a driven wheel (rear wheel of FF vehicle, front wheel of FR vehicle and RR vehicle). It can also be applied to a wheel support bearing unit. Further, in the example of the above-described embodiment, description has been made on the case where a tapered roller is used as the rolling element, but the rolling element may be a ball. Furthermore, in the structure shown in FIG. 1, as a structure of a sealing device that closes the open end of the internal space 18, in addition to the illustrated combination seal ring 19 a, for example, sealing as shown in FIGS. Devices 17c and 17d may be used. In the case of the structure (A), the metal core 24a is fitted and fixed to the inner peripheral surface of the outer end of the outer ring 1, and the seal lips 28a and 28a formed on the inner peripheral edge of the elastic member 25a are connected to the outer side of the inner ring 2a. It is brought into sliding contact with the flange 15 (or the inner flange 16 of the inner ring 2b). In the case of sliding contact with the outer flange 15, the axially outer seal lip 28a is prevented from interfering with the step surface 12a. In the case of the structure (B), the metal core 24b is fitted and fixed to the inner peripheral surface of the outer end of the outer ring 1, and the slinger 20a is externally attached to the outer flange 15 of the inner ring 2a (or the inner flange 16 of the inner ring 2b). Fit and fix. Then, the seal lip 28b of the elastic member 25b provided on the inner peripheral edge of the cored bar 24b is provided on the outer peripheral surface of the inner diameter side cylindrical portion 22 of the slinger 20a, and the elastic member 25c provided on the outer peripheral edge of the slinger 20a. The seal lips 28c, 28c are respectively brought into sliding contact with the inner peripheral surface of the outer diameter side cylindrical portion 26 and the outer surface of the inner ring portion 27 of the core metal 24b. When the slinger 20a is externally fixed to the outer flange 15, the outer ring portion 23 of the slinger 20a is prevented from interfering with the step surface 12a.

本発明の実施の形態の１例を示す半部断面図。The half part sectional view showing an example of an embodiment of the invention. 内部空間の開口端部を塞ぐ密封装置の別の２例を示す、部分断面図。The fragmentary sectional view which shows two other examples of the sealing device which block | closes the opening edge part of internal space. 従来構造の１例を示す断面図。Sectional drawing which shows an example of a conventional structure.

符号の説明Explanation of symbols

１ 外輪
２ａ、２ｂ 内輪
３ 円すいころ
４、４ａ ハブ
５ａ 第一の外輪軌道
５ｂ 第二の外輪軌道
６ 結合フランジ
７ａ 第一の内輪軌道
７ｂ 第二の内輪軌道
８ 保持器
９、９ａ 取付フランジ
１０ 円筒面部
１１ スプライン孔
１２、１２ａ 段差面
１３ 円筒部
１４ かしめ部
１５ 外側鍔部
１６ 内側鍔部
１７ａ、１７ｂ、１７ｃ、１７ｄ 密封装置
１８ 内部空間
１９ａ、１９ｂ 組み合わせシールリング
２０、２０ａ スリンガ
２１ シールリング
２２ 内径側円筒部
２３ 外側円輪部
２４、２４ａ、２４ｂ 芯金
２５、２５ａ、２５ｂ、２５ｃ 弾性材
２６ 外径側円筒部
２７ 内側円輪部
２８、２８ａ、２８ｂ、２８ｃ シールリップ
２９ 第二の段差面 DESCRIPTION OF SYMBOLS 1 Outer ring 2a, 2b Inner ring 3 Tapered roller 4, 4a Hub 5a First outer ring raceway 5b Second outer ring raceway 6 Connection flange 7a First inner ring raceway 7b Second inner ring raceway 8 Cage 9, 9a Mounting flange 10 Cylinder Surface portion 11 Spline hole 12, 12a Stepped surface 13 Cylindrical portion 14 Caulking portion 15 Outer flange portion 16 Inner flange portion 17a, 17b, 17c, 17d Sealing device 18 Internal space 19a, 19b Combination seal ring 20, 20a Slinger 21 Seal ring 22 Inner diameter Side cylindrical portion 23 Outer annular portion 24, 24a, 24b Core metal 25, 25a, 25b, 25c Elastic material 26 Outer diameter side cylindrical portion 27 Inner annular portion 28, 28a, 28b, 28c Seal lip 29 Second step surface

Claims (2)

内周面に複列の外輪軌道を形成した外輪と、それぞれの外周面に単列の内輪軌道を形成した１対の内輪と、これら各外輪軌道と各内輪軌道との間にそれぞれ複数個ずつ転動自在に設けた転動体と、外端寄り外周面に車輪を固定する為の取付フランジを、中間部乃至内端部外周面に上記両内輪を締め代を持たせて外嵌する円筒面部をそれぞれ形成した軸部材とを備え、上記１対の内輪のうちの外側に存在する一方の内輪を上記円筒面部に外嵌した状態で、この一方の内輪の外端面を、この軸部材の外周面で上記取付フランジの内側面と上記円筒面部との間に形成した段差面に突き当てている車輪支持用軸受ユニットに於いて、この段差面の外径を、上記一方の内輪の外端部の外径よりも大きくした事を特徴とする車輪支持用軸受ユニット。   An outer ring having a double row outer ring raceway formed on the inner peripheral surface, a pair of inner rings having a single row inner ring raceway formed on each outer peripheral surface, and a plurality of each between the outer ring raceways and the inner ring raceways. A rolling element provided so as to be able to roll, a mounting flange for fixing a wheel to the outer peripheral surface near the outer end, and a cylindrical surface part that fits the inner ring to the outer peripheral surface of the inner part or inner end part with a margin for tightening the inner rings. And the outer end surface of the one inner ring is connected to the outer periphery of the shaft member in a state in which one inner ring existing outside the pair of inner rings is fitted on the cylindrical surface portion. In a wheel support bearing unit that abuts against a stepped surface formed between the inner surface of the mounting flange and the cylindrical surface portion on the surface, the outer diameter of the stepped surface is set to the outer end portion of the one inner ring. Wheel support bearing unit characterized in that it is larger than the outer diameter. 外輪の外端部内周面と、一方の内輪の外端部外周面で内輪軌道から外れた部分に形成した鍔部との間に、スリンガとシールリングとを組み合わせて成る組み合わせシールリングを設けており、このうちのスリンガは、一方の内輪の鍔部に外嵌固定する内径側円筒部と、この内径側円筒部の外端縁から径方向外方に折れ曲った外側円輪部とから成り、上記シールリングは、外輪の外端部内周面に内嵌固定する外径側円筒部とこの外径側円筒部の内端縁から径方向内方に折れ曲った内側円輪部とから成る芯金と、上記外径側円筒部の内周面乃至上記内側円輪部の外側面に添着され、内周縁部に形成したシールリップを上記スリンガの一部に摺接させる弾性材とから成り、上記組み合わせシールリングを、上記スリンガの外側円輪部の外側面が上記一方の内輪の外端面よりも外方に突出しない状態で設置している、請求項１に記載した車輪支持用軸受ユニット。   A combination seal ring comprising a combination of a slinger and a seal ring is provided between the inner peripheral surface of the outer end of the outer ring and the flange formed on the outer peripheral surface of the outer end of one of the inner rings. Among these, the slinger is composed of an inner diameter side cylindrical portion that is fitted and fixed to the flange portion of one inner ring, and an outer ring portion that is bent radially outward from the outer end edge of the inner diameter side cylindrical portion. The seal ring comprises an outer diameter side cylindrical portion that is fitted and fixed to the inner peripheral surface of the outer end portion of the outer ring, and an inner ring portion that is bent radially inward from the inner end edge of the outer diameter side cylindrical portion. A cored bar and an elastic material attached to the inner peripheral surface of the outer cylindrical portion or the outer surface of the inner circular ring portion and slidably contacting a seal lip formed on the inner peripheral edge portion with a part of the slinger. , The combination seal ring, the outer surface of the outer ring portion of the slinger is the above Square of the outer end face of the inner ring are installed in a state that does not protrude outward, the wheel supporting bearing unit according to claim 1.
JP2005372864A 2005-12-26 2005-12-26 Wheel supporting bearing unit Pending JP2007168740A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2005372864A JP2007168740A (en) 2005-12-26 2005-12-26 Wheel supporting bearing unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005372864A JP2007168740A (en) 2005-12-26 2005-12-26 Wheel supporting bearing unit

Publications (1)

Publication Number Publication Date
JP2007168740A true JP2007168740A (en) 2007-07-05

Family

ID=38295872

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2005372864A Pending JP2007168740A (en) 2005-12-26 2005-12-26 Wheel supporting bearing unit

Country Status (1)

Country Link
JP (1) JP2007168740A (en)

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