JP2007271055A - Hub unit - Google Patents

Hub unit Download PDF

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Publication number
JP2007271055A
JP2007271055A JP2006100570A JP2006100570A JP2007271055A JP 2007271055 A JP2007271055 A JP 2007271055A JP 2006100570 A JP2006100570 A JP 2006100570A JP 2006100570 A JP2006100570 A JP 2006100570A JP 2007271055 A JP2007271055 A JP 2007271055A
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Japan
Prior art keywords
hub
axle
hub unit
end surface
attached
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Pending
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JP2006100570A
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Japanese (ja)
Inventor
Yoshibumi Shige
義文 重
Katsura Koyagi
桂 小八木
Kazuhisa Toda
一寿 戸田
Junji Murata
順司 村田
Shinichi Shirai
真一 白井
Masao Ikeda
昌生 池田
Masahiro Yuasa
正博 湯浅
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JTEKT Corp
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JTEKT Corp
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Priority to JP2006100570A priority Critical patent/JP2007271055A/en
Publication of JP2007271055A publication Critical patent/JP2007271055A/en
Pending legal-status Critical Current

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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
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • 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
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/507—Other types of ball or roller bearings with rolling elements journaled in one of the moving parts, e.g. stationary rollers to support a rotating part
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
    • 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
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • 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
    • 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
    • F16C19/30—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 axial load mainly
    • 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 damage to each member as part of a rolling bearing of a hub unit or the shorter life of the rolling bearing due to a great load on an axle in the axial direction. <P>SOLUTION: A space (t) formed between an end face 2a on the vehicle outer side of an outer ring 2 as part of the hub unit H<SB>1</SB>and an end face 11a on the vehicle inner side of a hub flange portion 11 in opposition to the end face 2a of the outer ring 2 is moderated so that one abuts on the other when a load F of 3G operates on the axle 14 in the axial direction. Even when the load F exceeding 3G operates thereon, the hub flange portion 11 is free from further displacement. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、車両（自動車）の懸架装置に取付けられ、車軸を回転可能に支承するためのハブユニットに関するものである。   The present invention relates to a hub unit that is attached to a suspension device of a vehicle (automobile) and rotatably supports an axle.

例えば凍結路を走行中の車両の車輪がロックして該車両が横すべりした場合や、走行中の車両の車輪が脱輪したり縁石に乗り上げたりした場合には、車軸のアキシャル方向に大きな負荷が作用する。そして、前記負荷は、ハブユニットを構成する転がり軸受にも及ぶ。   For example, when the wheel of a vehicle running on a frozen road locks and the vehicle slides sideways, or when the wheel of a running vehicle derails or rides on a curb, a large load is applied in the axial direction of the axle. Works. And the said load also reaches the rolling bearing which comprises a hub unit.

上記した負荷が転がり軸受に及んだ場合、該転がり軸受を構成する内外輪の軌道面に圧痕が生じ、車両の走行中に異音が発生したり、転がり軸受の寿命が短くなったりする。   When the above-described load is applied to the rolling bearing, indentations are generated on the raceway surfaces of the inner and outer rings constituting the rolling bearing, and abnormal noise is generated during traveling of the vehicle, and the life of the rolling bearing is shortened.

また、従来のハブユニットＨ’の場合、図６に示されるように、外輪５１における車両アウタ側の端面部５１ａと、ハブユニットＨ’を構成するハブフランジ部５２における車両インナ側の端面部５２ａとの間には、所定間隔ｔ’の隙間が形成されている。従来のハブユニットＨ’の場合、この間隔ｔ’が大きいため、前記隙間から入り込んだ雨水や異物が転がり軸受を腐食させたり、損傷させたりするおそれがある。これを防止するため、当該隙間の部分にシール材を取付ける技術が開示されている（特許文献１参照）。しかし、固定状態の外輪５２に対してハブフランジ５２が高速回転するため、前記シール材が抵抗となってしまい、車軸の回転に悪影響を及ぼす。
特開２００６−３７９７８号公報 Further, in the case of the conventional hub unit H ′, as shown in FIG. 6, an end surface portion 51 a on the vehicle outer side in the outer ring 51 and an end surface portion 52 a on the vehicle inner side in the hub flange portion 52 constituting the hub unit H ′. Is formed with a gap of a predetermined interval t ′. In the case of the conventional hub unit H ′, since this interval t ′ is large, rainwater and foreign matter entering from the gap may roll and corrode or damage the bearing. In order to prevent this, a technique for attaching a sealing material to the gap portion is disclosed (see Patent Document 1). However, since the hub flange 52 rotates at a high speed with respect to the outer ring 52 in a fixed state, the sealing material becomes a resistance and adversely affects the rotation of the axle.
JP 2006-37978 A

本発明は、上記した不具合に鑑み、車軸のアキシャル方向に大きな負荷が作用しても、ハブユニットに悪影響を及ぼさないようにすることを課題としている。   In view of the above-described problems, an object of the present invention is to prevent the hub unit from being adversely affected even when a large load acts in the axial direction of the axle.

課題を解決するための手段及び発明の効果Means for Solving the Problems and Effects of the Invention

上記した課題を解決するための請求項１の発明は、車両の懸架装置に回転不能に取付けられる筒状の外輪と、前記外輪の内周部に、複数個の転動体を介して外輪と同軸に配置される筒状の内輪と、前記内輪が嵌合装着されるハブに一体に取付けられる車軸とを備え、固定状態の懸架装置に対して、ハブを介して車軸を回転自在に支承するためのハブユニットであって、前記外輪の車両アウタ側の端面部と、前記ハブにおける車両アウタ側の端部にラジアル方向に張り出されたハブフランジ部の車両インナ側の端面部との間に形成される隙間の間隔が、車軸のアキシャル方向に所定の大きさの負荷が作用したときに当接するように調整されてなることを特徴としている。   In order to solve the above-mentioned problem, the invention of claim 1 includes a cylindrical outer ring that is non-rotatably attached to a vehicle suspension device, and is coaxial with the outer ring via a plurality of rolling elements on the inner periphery of the outer ring. A cylindrical inner ring disposed on the axle and an axle that is integrally attached to a hub to which the inner ring is fitted and mounted, and the axle is rotatably supported via the hub with respect to a fixed suspension device Between the end surface portion of the outer ring on the vehicle outer side and the end surface portion on the vehicle inner side of the hub flange portion projecting radially from the end portion of the hub on the vehicle outer side. The gap between the gaps is adjusted so as to come into contact when a predetermined load is applied in the axial direction of the axle.

請求項１の発明に係るハブユニットは、車軸のアキシャル方向に所定の大きさの負荷が作用したときに、外輪の車両アウタ側の端面部と、前記ハブにおける車両アウタ側の端部にラジアル方向に張り出されたハブフランジ部の車両インナ側の端面部と当接されるように、前記各端面部どうしの隙間の間隔が設定されてなる。このように、前記隙間を適正化することにより、所定の大きさの負荷（又はそれ以上の大きさの負荷）が車軸のアキシャル方向に作用した場合であっても、ハブユニットを構成する転がり軸受の各構成部材に悪影響を及ぼすことが回避され、走行中の車両から異音が発生することが防止されると共に、転がり軸受の寿命が短くなることが防止される。また、前記隙間を狭い範囲で適正化することにより、当該隙間の部分にラビリンス効果が奏され、雨水や異物の侵入が防止される。   In the hub unit according to the first aspect of the present invention, when a load having a predetermined magnitude is applied in the axial direction of the axle, the end surface portion of the outer ring on the vehicle outer side and the end portion of the hub on the vehicle outer side are arranged in the radial direction. The gaps between the respective end surface portions are set so as to come into contact with the end surface portion on the vehicle inner side of the hub flange portion projecting on the vehicle. In this way, by optimizing the gap, even when a predetermined load (or a larger load) acts in the axial direction of the axle, the rolling bearing constituting the hub unit. In this way, adverse effects on each of the components are avoided, the generation of abnormal noise from the traveling vehicle is prevented, and the life of the rolling bearing is prevented from being shortened. Further, by optimizing the gap in a narrow range, a labyrinth effect is produced in the gap portion, and rainwater and foreign matter are prevented from entering.

請求項２の発明は、請求項１の発明を前提として、前記各端面部の少なくとも一方側には、車軸のアキシャル方向に所定の大きさの負荷が作用したときに当接される他方側の端面部を、回転可能にして受けるための受圧部材が取付けられていることを特徴としている。   According to a second aspect of the present invention, on the premise of the first aspect of the present invention, at least one side of each of the end face portions is on the other side abutted when a predetermined load is applied in the axial direction of the axle. A pressure receiving member for receiving the end face portion in a rotatable manner is attached.

請求項２の発明では、双方の端面部が当接した場合であっても、少なくとも一方側の端面部には他方側の端面部を回転可能にして受けるための受圧部材が設けられているため、当接状態における車軸の回転が確保される。   In the invention of claim 2, even when both end face portions are in contact with each other, at least one end face portion is provided with a pressure receiving member for receiving the other end face portion in a rotatable manner. Rotation of the axle in the contact state is ensured.

請求項３の発明は、請求項２の発明を前提として、前記受圧部材は、前記端面部に予め定められた間隔で取付けられた複数個の針状部材であり、それらの長手方向を車軸のラジアル方向に配置させる形態で前記車軸の軸心を中心とする放射状に、かつそれぞれの針状部材が自身の軸心を中心に回転自在に取付けられていることを特徴としている。   According to a third aspect of the invention, on the premise of the second aspect of the invention, the pressure-receiving member is a plurality of needle-like members attached to the end face portion at a predetermined interval, and the longitudinal direction of the pressure-receiving member is the axis of the axle. In the form of being arranged in the radial direction, each needle-like member is attached radially so as to be centered on the axis of the axle and is rotatable about its own axis.

請求項３の発明では、当接される他方側の端面部が複数個の針状部材で受圧されるため、受圧面積が大きくなり、大きな負荷に対抗することができる。   In the invention of claim 3, since the end surface portion on the other side to be abutted is received by a plurality of needle-like members, the pressure receiving area is increased and a large load can be resisted.

請求項４の発明は、請求項２の発明を前提として、前記受圧部材は、前記端面部に予め定められた間隔で取付けられた複数個の玉であり、前記車軸の軸心を中心とする放射状に、かつそれぞれの玉が転動自在に取付けられていることを特徴としている。   According to a fourth aspect of the present invention, on the premise of the second aspect of the invention, the pressure receiving member is a plurality of balls attached to the end surface portion at a predetermined interval, and the shaft center of the axle is the center. It is characterized in that each ball is mounted in a radial manner so that it can roll freely.

請求項４の発明では、当接される他方側の端面部が複数個の玉で受圧されるため、車軸の回転抵抗が少なくて済む。   According to the fourth aspect of the present invention, since the end surface portion on the other side to be abutted is received by a plurality of balls, the rotational resistance of the axle can be reduced.

請求項５の発明は、請求項１ないし４のいずれかの発明を前提として、前記所定の大きさの負荷は、重力加速度の単位をＧとしたとき、３Ｇであることを特徴としている。   According to a fifth aspect of the present invention, on the premise of any one of the first to fourth aspects of the invention, the predetermined load is 3G when the unit of gravity acceleration is G.

請求項５の発明により、車軸のアキシャル方向に３Ｇの負荷が作用した場合であっても、ハブユニットの損傷が防止される。   According to the invention of claim 5, even if a 3G load is applied in the axial direction of the axle, damage to the hub unit is prevented.

請求項６の発明は、請求項１ないし５のいずれかの発明を前提として、前記隙間の間隔は、１ｍｍであることを特徴としている。   According to a sixth aspect of the present invention, on the premise of any of the first to fifth aspects, the gap is 1 mm.

請求項６の発明により、車軸のアキシャル方向に所定の大きさの負荷が作用した場合であっても、外輪又はハブユニットは１ｍｍまで変位することができる。   According to the sixth aspect of the present invention, even when a predetermined load is applied in the axial direction of the axle, the outer ring or the hub unit can be displaced up to 1 mm.

請求項７の発明は、請求項１ないし６のいずれかの発明を前提として、前記隙間にグリースが充填されていることを特徴としている。   The invention according to claim 7 is characterized in that the gap is filled with grease on the premise of any one of claims 1 to 6.

請求項７の発明では、ラビリンス効果がより確実に奏される。   In the invention of claim 7, the labyrinth effect is more reliably achieved.

本発明の実施例について説明する。   Examples of the present invention will be described.

図１は本発明の第１実施例のハブユニットＨ１の断面図、図２は図１の要部の拡大図である。最初に、本発明の第１実施例のハブユニットＨ１について説明する。図１に示されるように、懸架装置を構成するナックル１に、回転不能にして外輪２が固着されている。前記外輪２の内周部には、複数個の転動体３（玉）を介して２個の内輪（アウタ側内輪４とインナ側内輪５）が配置されている。ここで、車両の外側（図１の図面視における左側）を「アウタ側」と記載し、同じく内側を「インナ側」と記載する。各内輪４，５は段付き形状を呈していて、複数個の転動体３を保持して転動体列を構成するための冠型の保持器１０が取付けられる小径部６と、転動体３の外径に対応する曲面形状に設けられた軌道面７を介して前記小径部６と連続する大径部８とから成り、いずれも同一形状である。各内輪４，５は、それらの小径部６の端面（アウタ側内輪４のインナ側端面とインナ側内輪５のアウタ側端面）どうしが対向して当接配置された直列状態で、複列となってハブ９のハブ本体部９ａに嵌合装着される。この状態で、アウタ側内輪４のアウタ側端面は、ハブ９の内輪当接面９ｂに当接されると共に、インナ側内輪５のインナ側端面は、ハブ９の一端部（内側の端面）から僅かに突出される。 1 is a sectional view of the hub unit H 1 of the first embodiment of the present invention, FIG. 2 is an enlarged view of a main part of FIG. First, a description will be given of the hub unit H 1 of the first embodiment of the present invention. As shown in FIG. 1, an outer ring 2 is fixed to a knuckle 1 constituting a suspension device in a non-rotatable manner. Two inner rings (an outer side inner ring 4 and an inner side inner ring 5) are arranged on the inner peripheral portion of the outer ring 2 via a plurality of rolling elements 3 (balls). Here, the outer side of the vehicle (left side in the drawing view of FIG. 1) is referred to as “outer side”, and the inner side is also referred to as “inner side”. Each of the inner rings 4 and 5 has a stepped shape, a small-diameter portion 6 to which a crown-shaped cage 10 for holding a plurality of rolling elements 3 and constituting a rolling element row is attached, and the rolling elements 3 The small-diameter portion 6 and the large-diameter portion 8 are continuous through a raceway surface 7 provided in a curved shape corresponding to the outer diameter, and both have the same shape. The inner rings 4 and 5 are arranged in series in which the end surfaces of the small-diameter portions 6 (the inner side end surface of the outer side inner ring 4 and the outer side end surface of the inner side inner ring 5) are arranged in contact with each other. Thus, the hub 9 is fitted and mounted on the hub body 9a. In this state, the outer side end surface of the outer side inner ring 4 is in contact with the inner ring contact surface 9b of the hub 9, and the inner side end surface of the inner side inner ring 5 is from one end (inner end surface) of the hub 9. Slightly protruding.

前記ハブ９は、各内輪４，５が嵌合装着されるハブ本体部９ａと、アウタ側内輪４のアウタ側端面が当接される内輪当接面９ｂを介してラジアル方向に張り出して形成されたハブフランジ部１１とから成る。前記ハブフランジ部１１の周縁部には、複数本のボルト孔１１ａがハブ９のアキシャル方向に沿って設けられている。各ボルト孔１１ａに挿通されたボルト１２により、前記ハブ９とホイール（図示せず）とが一体に組み付けられる。また、前記ハブ本体部９ａの軸心部分にはスプライン孔１３が設けられていて、該スプライン孔１３に、段付き形状に形成された車軸１４がスプライン嵌合される。前記車軸１４は、車軸本体部１４ａと、該車軸本体部１４ａよりも小径で、スプラインが形成されたハブ装着部１４ｂとから成る。車軸１４のハブ装着部１４ｂがハブ９にスプライン嵌合されたとき、その先端部がハブ９の他端部から突出される。そして、当該突出部分にナット１５が螺合される。このとき、車軸１４の段差面（内輪当接面１４ｃ）が、ハブ９に嵌合装着されたインナ側内輪５のインナ側端面を押圧する。これにより、ハブ９と車軸１４が一体に取付けられ、駆動回転される車軸１４の駆動力が、ハブ９を介してホイールに伝達される。   The hub 9 is formed to project in the radial direction via a hub main body portion 9a to which each of the inner rings 4 and 5 is fitted and mounted, and an inner ring contact surface 9b to which the outer side end surface of the outer side inner ring 4 is contacted. And a hub flange portion 11. A plurality of bolt holes 11 a are provided in the peripheral direction of the hub flange portion 11 along the axial direction of the hub 9. The hub 9 and a wheel (not shown) are assembled together by bolts 12 inserted into the respective bolt holes 11a. Further, a spline hole 13 is provided in the shaft center portion of the hub main body 9a, and an axle 14 formed in a stepped shape is spline fitted into the spline hole 13. The axle 14 includes an axle body 14a and a hub mounting portion 14b having a smaller diameter than the axle body 14a and having a spline formed thereon. When the hub mounting portion 14 b of the axle 14 is spline-fitted to the hub 9, the tip end portion projects from the other end portion of the hub 9. And the nut 15 is screwed by the said protrusion part. At this time, the stepped surface (inner ring contact surface 14 c) of the axle 14 presses the inner side end surface of the inner side inner ring 5 fitted to the hub 9. As a result, the hub 9 and the axle 14 are integrally attached, and the driving force of the axle 14 that is driven and rotated is transmitted to the wheel via the hub 9.

第１実施例のハブユニットＨ１の場合、外輪２におけるハブフランジ部１１と対向する側の端部が、車軸１４のアキシャル方向に沿って延設されていて、外輪２におけるアウタ側の端面部２ａとハブフランジ部１１におけるインナ側の端面部１１ｂとの間には、通常の状態（車軸１４にアキシャル方向の負荷が作用していない状態）で、所定間隔ｔ（本実施例の場合、１ｍｍ）を有する隙間が形成されている。前記隙間の間隔ｔは、車軸１４のアキシャル方向に大きな負荷Ｆが作用したときに、両端面部２ａ，１１ｂが相互に当接されるだけの間隔に適正化されている。なお、前記アキシャル方向の負荷は、アウタ側からインナ側に作用する場合と、インナ側からアウタ側に作用する場合とがある。また、図２においては、ボルト孔１１ａ及びボルト１２の図示を省略してある。 In the case of the hub unit H 1 of the first embodiment, the end of the outer ring 2 on the side facing the hub flange 11 extends along the axial direction of the axle 14, and the outer end face of the outer ring 2 is located on the outer side. 2a and the end surface portion 11b on the inner side of the hub flange portion 11 in a normal state (a state in which no axial load is applied to the axle 14), a predetermined interval t (1 mm in this embodiment) ) Is formed. The interval t of the gap is optimized so that both end portions 2a and 11b are brought into contact with each other when a large load F is applied in the axial direction of the axle 14. The axial load may be applied from the outer side to the inner side, or may be applied from the inner side to the outer side. Moreover, in FIG. 2, illustration of the bolt hole 11a and the volt | bolt 12 is abbreviate | omitted.

そして、前記大きな負荷Ｆとは、重力加速度の単位をＧとしたときに３Ｇで表示される大きさの負荷である。ここで、１Ｇは、９．８ｍ／ｓ２である。即ち、車軸１４のアキシャル方向に、車両のアウタ側からインナ側に向かう３Ｇの負荷Ｆが作用したとき、ハブフランジ部１１が外輪２に接近し、両者の端面部２ａ，１１ｂが当接する。その状態を、図２において二点鎖線で示す。これにより、車軸１４のアキシャル方向に３Ｇ（又はそれ以上）の負荷Ｆが作用しても、ハブフランジ部１１は隙間の間隔ｔ以上に変位せず、ハブユニットＨ１が損傷することが防止される。換言すれば、前記隙間の間隔ｔは、車軸１４のアキシャル方向に大きさが３Ｇの負荷Ｆが作用したときに、外輪２及びハブフランジ部１１の各端面部２ａ，１１ｂが相互に接近して当接されるように設定されている。 The large load F is a load having a size displayed in 3G when the unit of gravity acceleration is G. Here, 1G is 9.8 m / s 2 . That is, when a 3G load F is applied in the axial direction of the axle 14 from the outer side to the inner side of the vehicle, the hub flange portion 11 approaches the outer ring 2 and both end surface portions 2a and 11b abut against each other. This state is indicated by a two-dot chain line in FIG. Thus, even when acting load F is 3G the axial direction of the axle 14 (or more), the hub flange 11 is not displaced more than the interval t of the gap, it is possible to prevent the hub unit H 1 is damaged The In other words, when the load F having a size of 3 G acts in the axial direction of the axle 14, the gap t is set so that the end surfaces 2 a and 11 b of the outer ring 2 and the hub flange portion 11 approach each other. It is set to abut.

更に、前記隙間の間隔ｔが微小であるため、隙間の部分にラビリンス効果が奏され、当該隙間から雨水や異物が入り込むおそれが少なくなる。これにより、ハブユニットＨ１の損傷が、更に確実に防止される。そして、前記隙間の部分にグリースを充填することにより、車軸１４の回転を損なうことなく前記ラビリンス効果がより効果的に奏される。 Furthermore, since the gap t is very small, a labyrinth effect is produced in the gap, and the possibility of rainwater and foreign matter entering through the gap is reduced. Thus, damage of the hub unit H 1 is more reliably prevented. By filling the gap with grease, the labyrinth effect is more effectively achieved without impairing the rotation of the axle 14.

次に、第２実施例のハブユニットＨ２について説明する。第２実施例のハブユニットＨ２は、図３及び図４に示されるように、外輪２におけるハブフランジ部１１と対向する端面部２ａに、周方向に一定の角度をおいて所定個数（第２実施例の場合、３６個）の針状部材１６（受圧部材）が取付けられている。各針状部材１６は、それらの長手方向を車軸１４のラジアル方向に配置させる形態で、車軸１４の軸心を中心とする放射状に、かつそれぞれの針状部材１６が自身の軸心を中心に回転自在に取付けられている。そして、各針状部材１６の外周面と対向するハブフランジ部１１の端面部１１ｂとの間に形成される隙間の間隔ｔが、車軸のアキシャル方向に所定の大きさの負荷が作用したときに当接されるように形成されている。第２実施例のハブユニットＨ２の場合、前記間隔ｔは、第１実施例のハブユニットＨ１の場合と同様に１ｍｍである。 It will now be described hub unit of H 2 second embodiment. As shown in FIGS. 3 and 4, the hub unit H 2 according to the second embodiment has a predetermined number (a first number) of the end surface portion 2 a facing the hub flange portion 11 in the outer ring 2 at a certain angle in the circumferential direction. In the case of the second embodiment, 36 pieces of needle-like members 16 (pressure receiving members) are attached. The needle-like members 16 are arranged in such a manner that their longitudinal directions are arranged in the radial direction of the axle 14, and are radially centered on the axis of the axle 14, and each needle-like member 16 is centered on its own axis. It is rotatably mounted. And when the load t of the predetermined magnitude | size acts in the axial direction of an axle shaft, the space | interval t of the clearance gap formed between the outer peripheral surface of each needle-like member 16 and the end surface part 11b of the hub flange part 11 is opposed. It is formed so as to abut. For the hub unit of H 2 second embodiment, the distance t is 1mm as in the case of the hub unit H 1 of the first embodiment.

通常の状態で、ハブフランジ部１１の端面部１１ｂと各針状部材１６の外周面との間には、隙間が形成されているため、車軸１４の回転に支障はない。そして、第１実施例のハブユニットＨ１の場合と同様に、車軸１４のアキシャル方向に大きさが３Ｇの負荷Ｆが作用したときに、各針状部材１６の各外周面とハブフランジ部１１の端面部１１ｂが相互に接近して当接されるように設定されている。これにより、車軸１４のアキシャル方向に３Ｇ（又はそれ以上）の負荷Ｆが作用しても、ハブフランジ部１１は隙間の間隔ｔ以上に変位せず、ハブユニットＨ１が損傷することが防止される。そして、両者が当接した場合であっても、各針状部材１６が自身の軸心を中心に回転自在に取付けられていて、それらがスラストころ軸受として作用するため、前記負荷Ｆを受圧すると共に、それらが車軸１４の回転の抵抗となることもない。また、各針状部材１６によって、隙間の部分にラビリンス効果が奏されるため、当該隙間から雨水や異物が入り込むことが防止される。 Since a gap is formed between the end surface portion 11b of the hub flange portion 11 and the outer peripheral surface of each needle-like member 16 in a normal state, there is no hindrance to the rotation of the axle 14. Then, as in the case of the hub unit H 1 of the first embodiment, when a load F having a size of 3 G acts in the axial direction of the axle 14, each outer peripheral surface of each needle-like member 16 and the hub flange portion 11. The end face portions 11b are set so as to approach each other and come into contact with each other. Thus, even when acting load F is 3G the axial direction of the axle 14 (or more), the hub flange 11 is not displaced more than the interval t of the gap, it is possible to prevent the hub unit H 1 is damaged The And even if both contact | abut, each needle-like member 16 is rotatably attached centering on its own shaft center, and since they act as a thrust roller bearing, the said load F is received. At the same time, they do not become resistance to rotation of the axle 14. Moreover, since the labyrinth effect is show | played by the part of a clearance gap by each acicular member 16, rainwater and a foreign material are prevented from entering from the clearance gap.

第３実施例のハブユニットＨ３は、図５に示されるように、受圧部材が所定個数（第３実施例の場合、３６個）の玉１７の場合である。第３実施例のハブユニットＨ３の場合にも、第２実施例のハブユニットＨ２と同様の効果が奏される。 As shown in FIG. 5, the hub unit H 3 of the third embodiment is a case where the pressure receiving member is a predetermined number of balls 17 (36 in the case of the third embodiment). In the case of the hub unit H 3 of the third embodiment, the same effect as the hub unit of H 2 second embodiment it is achieved.

上記した第２及び第３の各実施例のハブユニットＨ２，Ｈ３においては、外輪２の端面部２ａに受圧部材（針状部材１５、玉１６）が取付けられている。しかし、前記受圧部材をハブフランジ部１１の端面部１１ｂに、或いは双方に取付けてもよい。 In the hub units H 2 and H 3 of the second and third embodiments described above, a pressure receiving member (the needle-like member 15 and the ball 16) is attached to the end surface portion 2 a of the outer ring 2. However, you may attach the said pressure receiving member to the end surface part 11b of the hub flange part 11, or both.

上記した各実施例のハブユニットＨ１〜Ｈ３における外輪２とハブフランジ部１１との隙間の間隔ｔは、１ｍｍである。しかし、ハブユニットＨ１〜Ｈ３の損傷を確実に防止するため、間隔ｔはそれより小さくてもよい。 The gap t between the outer ring 2 and the hub flange portion 11 in the hub units H 1 to H 3 of the above-described embodiments is 1 mm. However, in order to prevent damage to the hub units H 1 to H 3 with certainty, the interval t may be smaller than that.

本発明の第１実施例のハブユニットＨ１の断面図である。It is sectional drawing of hub unit H1 of 1st Example of this invention. 図１の要部の拡大図である。It is an enlarged view of the principal part of FIG. 第２実施例のハブユニットＨ２の断面図である。It is sectional drawing of hub unit H2 of 2nd Example. ハブユニットＨ２の要部の側面断面図である。It is a side sectional view of a main portion of the hub unit H 2. 第３実施例のハブユニットＨ３の要部の側面断面図である。It is side surface sectional drawing of the principal part of hub unit H3 of 3rd Example. 従来のハブユニットＨ’の要部の断面図である。It is sectional drawing of the principal part of the conventional hub unit H '.

符号の説明Explanation of symbols

Ｈ１〜Ｈ３：ハブユニット
Ｆ：負荷
ｔ：間隔
１：ナックル（懸架装置）
２：外輪
２ａ：端面部
３：転動体
４：アウタ側内輪
５：インナ側内輪
７：軌道面
９：ハブ
１１：ハブフランジ部
１１ｂ：端面部
１４：車軸
１６：針状部材（受圧部材）
１７：玉（受圧部材） H 1 to H 3 : Hub unit
F: Load
t: Interval
1: Knuckle (suspension device)
2: Outer ring
2a: End face part
3: Rolling element
4: Outer side inner ring
5: Inner side inner ring
7: Track surface
9: Hub
11: Hub flange part 11b: End face part
14: Axle
16: Needle-shaped member (pressure receiving member)
17: Ball (pressure receiving member)

Claims (7)

車両の懸架装置に回転不能に取付けられる筒状の外輪と、
前記外輪の内周部に、複数個の転動体を介して外輪と同軸に配置される筒状の内輪と、
前記内輪が嵌合装着されるハブに一体に取付けられる車軸とを備え、
固定状態の懸架装置に対して、ハブを介して車軸を回転自在に支承するためのハブユニットであって、
前記外輪の車両アウタ側の端面部と、前記ハブにおける車両アウタ側の端部にラジアル方向に張り出されたハブフランジ部の車両インナ側の端面部との間に形成される隙間の間隔が、車軸のアキシャル方向に所定の大きさの負荷が作用したときに当接するように調整されてなることを特徴とするハブユニット。 A cylindrical outer ring that is non-rotatably attached to a vehicle suspension;
A cylindrical inner ring disposed coaxially with the outer ring via a plurality of rolling elements on the inner periphery of the outer ring,
An axle mounted integrally with a hub to which the inner ring is fitted and mounted,
A hub unit for rotatably supporting an axle via a hub with respect to a fixed suspension device,
A gap formed between an end surface portion on the vehicle outer side of the outer ring and an end surface portion on the vehicle inner side of a hub flange portion protruding in a radial direction at an end portion on the vehicle outer side of the hub, A hub unit, wherein the hub unit is adjusted so as to come into contact when a predetermined load is applied in an axial direction of an axle. 前記各端面部の少なくとも一方側には、車軸のアキシャル方向に所定の大きさの負荷が作用したときに当接される他方側の端面部を、回転可能にして受けるための受圧部材が取付けられていることを特徴とする請求項１に記載のハブユニット。   At least one side of each of the end surface portions is attached with a pressure receiving member for rotatably receiving the other end surface portion that comes into contact when a predetermined load is applied in the axial direction of the axle. The hub unit according to claim 1, wherein the hub unit is provided. 前記受圧部材は、前記端面部に予め定められた間隔で取付けられた複数個の針状部材であり、それらの長手方向を車軸のラジアル方向に配置させる形態で前記車軸の軸心を中心とする放射状に、かつそれぞれの針状部材が自身の軸心を中心に回転自在に取付けられていることを特徴とする請求項２に記載のハブユニット。   The pressure-receiving member is a plurality of needle-like members attached to the end face portion at a predetermined interval, and the longitudinal direction of the pressure-receiving members is arranged in the radial direction of the axle so as to be centered on the axle center of the axle. The hub unit according to claim 2, wherein each needle-like member is attached in a radial manner so as to be rotatable about its own axis. 前記受圧部材は、前記端面部に予め定められた間隔で取付けられた複数個の玉であり、前記車軸の軸心を中心とする放射状に、かつそれぞれの玉が転動自在に取付けられていることを特徴とする請求項２に記載のハブユニット。   The pressure receiving member is a plurality of balls attached to the end face portion at a predetermined interval, and each ball is attached in a radial manner about the axis of the axle and is freely rotatable. The hub unit according to claim 2, wherein: 前記所定の大きさの負荷は、重力加速度の単位をＧとしたとき、３Ｇであることを特徴とする請求項１ないし４のいずれかに記載のハブユニット。   The hub unit according to any one of claims 1 to 4, wherein the load having the predetermined magnitude is 3G when a unit of gravity acceleration is G. 前記隙間の間隔は、１ｍｍであることを特徴とする請求項１ないし５のいずれかに記載のハブユニット。   The hub unit according to claim 1, wherein the gap is 1 mm. 前記隙間にグリースが充填されていることを特徴とする請求項１ないし６のいずれかに記載のハブユニット。   The hub unit according to any one of claims 1 to 6, wherein the gap is filled with grease.
JP2006100570A 2006-03-31 2006-03-31 Hub unit Pending JP2007271055A (en)

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Cited By (7)

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US20110243487A1 (en) * 2010-04-05 2011-10-06 GM Global Technology Operations LLC Apparatus with secondary load path for vehicle wheel bearing assembly and feature to inhibit corrosion
US20150010260A1 (en) * 2008-11-06 2015-01-08 Kyklos Bearing International, Llc Wheel Bearing Assembly
WO2017076401A1 (en) * 2015-11-02 2017-05-11 Schaeffler Technologies AG & Co. KG Wheel bearing unit
WO2019107371A1 (en) * 2017-11-28 2019-06-06 Ntn株式会社 Hub unit having steering function, and vehicle provided with said hub unit
US10464370B2 (en) 2015-11-02 2019-11-05 Schaeffler Technologies AG & Co. KG Wheel bearing unit
JP2019214369A (en) * 2019-07-31 2019-12-19 Ntn株式会社 Hub bearing with steering shaft and hub unit with steering function

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Publication number Priority date Publication date Assignee Title
EP2184181B2 (en) † 2008-11-06 2020-03-11 SKF USA Inc. Wheel bearing assembly
US8845203B2 (en) 2008-11-06 2014-09-30 Kyklos Bearing International, Inc. Wheel bearing assembly
US20150010260A1 (en) * 2008-11-06 2015-01-08 Kyklos Bearing International, Llc Wheel Bearing Assembly
US9283808B2 (en) * 2008-11-06 2016-03-15 Kyklos Bearing International, Llc Wheel bearing assembly
JP2010111386A (en) * 2008-11-06 2010-05-20 Kyklos Bearing Internatl Inc Wheel bearing assembly
US20110243487A1 (en) * 2010-04-05 2011-10-06 GM Global Technology Operations LLC Apparatus with secondary load path for vehicle wheel bearing assembly and feature to inhibit corrosion
US8740468B2 (en) * 2010-04-05 2014-06-03 GM Global Technology Operations LLC Apparatus with secondary load path for vehicle wheel bearing assembly and feature to inhibit corrosion
WO2017076401A1 (en) * 2015-11-02 2017-05-11 Schaeffler Technologies AG & Co. KG Wheel bearing unit
US10464370B2 (en) 2015-11-02 2019-11-05 Schaeffler Technologies AG & Co. KG Wheel bearing unit
JP2019094032A (en) * 2017-11-28 2019-06-20 Ntn株式会社 Hub unit with steering function and vehicle equipped with same
WO2019107371A1 (en) * 2017-11-28 2019-06-06 Ntn株式会社 Hub unit having steering function, and vehicle provided with said hub unit
US11565548B2 (en) 2017-11-28 2023-01-31 Ntn Corporation Hub unit having steering function, and vehicle provided with said hub unit
JP2019214369A (en) * 2019-07-31 2019-12-19 Ntn株式会社 Hub bearing with steering shaft and hub unit with steering function

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