JP5207845B2 - Drive wheel bearing device - Google Patents

Drive wheel bearing device Download PDF

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JP5207845B2
JP5207845B2 JP2008161690A JP2008161690A JP5207845B2 JP 5207845 B2 JP5207845 B2 JP 5207845B2 JP 2008161690 A JP2008161690 A JP 2008161690A JP 2008161690 A JP2008161690 A JP 2008161690A JP 5207845 B2 JP5207845 B2 JP 5207845B2
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joint member
diameter
annular plate
outer joint
raceway surface
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JP2010000916A (en
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賢二 山田
充孝 山田
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NTN Corp
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NTN 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • 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)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、例えば自動車の懸架装置に対して駆動車輪（ＦＦ車の前輪、ＦＲ車の後輪、４ＷＤ車の全輪）を回転自在に支持する駆動車輪用軸受装置に関する。   The present invention relates to a drive wheel bearing device that rotatably supports drive wheels (front wheels of FF vehicles, rear wheels of FR vehicles, all wheels of 4WD vehicles), for example, with respect to a suspension system of an automobile.

自動車の軸受装置には、従動車輪用と駆動車輪用があり、それぞれの用途に応じて種々の形式のものが提案されている。例えば、図９は駆動車輪用軸受装置を例示する。この軸受装置は、ハブ輪１１０および内輪１２０ａ，１２０ｂ、複列の転動体１３０，１４０、外輪１５０、等速自在継手１６０を主要な構成要素としている。   There are two types of bearing devices for automobiles, one for a driven wheel and one for a drive wheel. Various types of bearing devices have been proposed according to the respective applications. For example, FIG. 9 illustrates a drive wheel bearing device. The bearing device includes a hub wheel 110 and inner rings 120a and 120b, double-row rolling elements 130 and 140, an outer ring 150, and a constant velocity universal joint 160 as main components.

ハブ輪１１０は、そのアウトボード側の端部に、車輪（図示せず）を取り付けるための車輪取付フランジ１１４を備えている。この車輪取付フランジ１１４の円周方向等間隔に、ホイールディスクを固定するためのハブボルト１１６が植設されている。   The hub wheel 110 includes a wheel mounting flange 114 for mounting a wheel (not shown) at an end portion on the outboard side. Hub bolts 116 for fixing the wheel disc are implanted at equal intervals in the circumferential direction of the wheel mounting flange 114.

このハブ輪１１０の外周面に一対の内輪１２０ａ，１２０ｂを嵌合させ、一方の内輪１２０ａの外周面にアウトボード側の内側軌道面１２２ａが形成され、他方の内輪１２０ｂの外周面にインボード側の内側軌道面１２２ｂが形成されている。これらアウトボード側の内側軌道面１２２ａとインボード側の内側軌道面１２２ｂとで複列の内側軌道面を構成している。このハブ輪１１０の軸孔の内周面には、後述の等速自在継手１６０をトルク伝達可能に連結するための雌スプライン１１１が形成されている。   A pair of inner rings 120a and 120b are fitted to the outer peripheral surface of the hub wheel 110, an inner raceway surface 122a on the outboard side is formed on the outer peripheral surface of one inner ring 120a, and the inboard side is formed on the outer peripheral surface of the other inner ring 120b. The inner raceway surface 122b is formed. The outboard side inner raceway surface 122a and the inboard side inner raceway surface 122b constitute a double row inner raceway surface. On the inner peripheral surface of the shaft hole of the hub wheel 110, a female spline 111 for connecting a constant velocity universal joint 160, which will be described later, so as to transmit torque is formed.

外輪１５０は、内周面に内輪１２０ａ，１２０ｂの内側軌道面１２２ａ，１２２ｂと対向する複列の外側軌道面１５２，１５４が形成され、車体（図示せず）に取り付けるための車体取付フランジ１５６を備えている。この車体取付フランジ１５６は、車体の懸架装置（図示せず）から延びるナックルに取り付け孔１５８を利用してボルト等で固定される。   The outer ring 150 has double rows of outer raceway surfaces 152 and 154 facing the inner raceway surfaces 122a and 122b of the inner races 120a and 120b on the inner circumferential surface, and a vehicle body mounting flange 156 for mounting to a vehicle body (not shown). I have. The vehicle body attachment flange 156 is fixed to a knuckle extending from a vehicle suspension system (not shown) with a bolt or the like using an attachment hole 158.

軸受部１７０は、複列のアンギュラ玉軸受構造で、内輪１２０ａ，１２０ｂの外周面に形成された内側軌道面１２２ａ，１２２ｂと外輪１５０の内周面に形成された外側軌道面１５２，１５４との間に転動体１３０，１４０を介在させ、各列の転動体１３０，１４０を保持器１３２，１４２により円周方向等間隔に回転自在に保持した構造を有する。   The bearing portion 170 has a double-row angular contact ball bearing structure, and includes inner raceway surfaces 122a and 122b formed on the outer peripheral surface of the inner rings 120a and 120b and outer raceway surfaces 152 and 154 formed on the inner peripheral surface of the outer ring 150. The rolling elements 130 and 140 are interposed therebetween, and the rolling elements 130 and 140 in each row are rotatably held by the cages 132 and 142 at equal intervals in the circumferential direction.

軸受部１７０の両端開口部には、内輪１２０ａ，１２０ｂの外周面に摺接するように、外輪１５０と内輪１２０ａ，１２０ｂとの環状空間を密封する一対のシール１３４，１４４が外輪１５０の両端部内径に嵌合され、内部に充填された潤滑剤の漏洩ならびに外部からの水や異物の侵入を防止するようになっている。   A pair of seals 134 and 144 for sealing the annular space between the outer ring 150 and the inner rings 120a and 120b are formed at both end openings of the bearing part 170 so as to be in sliding contact with the outer peripheral surfaces of the inner rings 120a and 120b. And prevents leakage of the lubricant filled in the inside and intrusion of water and foreign matters from the outside.

前述したハブ輪１１０に等速自在継手１６０の外側継手部材１６２を連結することにより、軸受装置が構成される。等速自在継手１６０の外側継手部材１６２は、ドライブシャフトを構成する中間軸（図示せず）の一端に設けられ、内側継手部材、ボールおよびケージからなる内部部品（図示せず）を収容したカップ状のマウス部１６４と、そのマウス部１６４の基部から軸方向に一体に延びるステム部１６６とで構成されている。このステム部１６６の外周面には、前述のハブ輪１１０をトルク伝達可能に連結するための雄スプライン１６８が形成されている。   A bearing device is configured by connecting the outer joint member 162 of the constant velocity universal joint 160 to the hub wheel 110 described above. The outer joint member 162 of the constant velocity universal joint 160 is provided at one end of an intermediate shaft (not shown) constituting the drive shaft, and accommodates an internal part (not shown) composed of an inner joint member, a ball and a cage. And a stem portion 166 extending integrally from the base portion of the mouse portion 164 in the axial direction. On the outer peripheral surface of the stem portion 166, a male spline 168 for connecting the hub wheel 110 described above so as to be able to transmit torque is formed.

この外側継手部材１６２のステム部１６６をハブ輪１１０の軸孔に圧入し、ステム部１６６の外周面に形成された雄スプライン１６８とハブ輪１１０の軸孔内周面に形成された雌スプライン１１１を嵌合させることにより、トルク伝達可能となっている。また、内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との対向面とを突き合わせた状態で、ステム部１６６の端部に形成された雄ねじ部１６５にナット１７２を締め付けることによって、等速自在継手１６０をハブ輪１１０に固定する。このナットによる締め付け力（軸力）でもって軸受部１７０に予圧を付与している。   The stem portion 166 of the outer joint member 162 is press-fitted into the shaft hole of the hub wheel 110, and the male spline 168 formed on the outer peripheral surface of the stem portion 166 and the female spline 111 formed on the inner peripheral surface of the shaft hole of the hub wheel 110. The torque can be transmitted by fitting. Further, the nut 172 is fastened to the male thread portion 165 formed at the end portion of the stem portion 166 in a state where the facing surface of the inboard side end portion 124b of the inner ring 120b and the shoulder portion 161 of the outer joint member 162 abut each other. Thus, the constant velocity universal joint 160 is fixed to the hub wheel 110. A preload is applied to the bearing portion 170 with a tightening force (axial force) by the nut.

ところで、前述した駆動輪用軸受装置では、軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１とが突き合わされた接触状態にあることから、例えば車両発進時、軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との間で、カッキン音と通称されるスティックスリップ音が発生するおそれがある。   Incidentally, in the drive wheel bearing device described above, the inboard side end portion 124b of the inner ring 120b of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162 are in contact with each other. There is a possibility that a stick-slip sound, commonly referred to as a cuckling noise, may be generated between the inboard side end portion 124b of the inner ring 120b of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162.

このスティックスリップ音は、車両発進時、静止状態にある軸受部１７０の内輪１２０ｂに対して等速自在継手１６０の外側継手部材１６２から回転トルクが負荷されると、雌雄スプライン１１１，１６８を介して外側継手部材１６２からハブ輪１１０へ回転トルクを伝達しようとするが、外側継手部材１６２と軸受部１７０との間の伝達トルク変動と外側継手部材１６２のねじれにより、内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との間で急激な滑りが発生する。この急激な滑りが原因となってスティックスリップ音が発生する。   This stick-slip noise is transmitted through the male and female splines 111 and 168 when a rotational torque is applied from the outer joint member 162 of the constant velocity universal joint 160 to the inner ring 120b of the bearing portion 170 in a stationary state when the vehicle starts. An attempt is made to transmit rotational torque from the outer joint member 162 to the hub wheel 110, but the inboard side end portion of the inner ring 120 b is caused by transmission torque fluctuation between the outer joint member 162 and the bearing portion 170 and torsion of the outer joint member 162. A sudden slip occurs between 124b and the shoulder 161 of the outer joint member 162. This sudden slip causes stick-slip noise.

前述したスティックスリップ音を未然に防止する手段として、軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との対向面間に、摺動特性の優れた材料をコーティングしたプレートを挟み込む手段（例えば、特許文献１，２参照）が講じられている。   As a means for preventing the above-described stick-slip noise, a material having excellent sliding characteristics is provided between the facing surfaces of the inboard side end portion 124b of the inner ring 120b of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162. Means (for example, see Patent Documents 1 and 2) for sandwiching the coated plate is taken.

これら特許文献１，２では、軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との対向面間に前述のプレートを介在させることにより、その軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との間での摩擦抵抗を小さくして積極的な滑りが生じるようにして、急激な滑りを発生させることなく、スティックスリップ音が発生しないようにしている。
特開２００３−９７５８８号公報 特表２００７−５０８９８６号公報 In these Patent Documents 1 and 2, the above-described plate is interposed between the opposed surfaces of the inboard side end portion 124 b of the inner ring 120 b of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162. The slip resistance is reduced without causing a sudden slip by reducing the frictional resistance between the inboard side end portion 124b of the inner ring 120b and the shoulder portion 161 of the outer joint member 162, thereby generating a positive slip. The sound is not generated.
JP 2003-97588 A Special table 2007-508986 gazette

ところで、特許文献１，２に開示された軸受装置では、前述したように、軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との対向面間に、摺動特性の優れた材料でコーティングされた環状のプレートを介在させることにより、スティックスリップ音の発生を未然に防止するようにしている。   By the way, in the bearing devices disclosed in Patent Documents 1 and 2, as described above, the sliding between the opposing surfaces of the inboard side end portion 124b of the inner ring 120b of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162 is performed. Generation of stick-slip noise is prevented by interposing an annular plate coated with a material having excellent dynamic characteristics.

しかしながら、前述した特許文献１，２のいずれも、ナット１７２の締め付けにより軸力を確保し、軸受部１７０に予圧を付与する構造を具備していることから、軸受部１７０の内輪１２０ｂのインボード側端部１２４ｂと外側継手部材１６２の肩部１６１との対向面間に介在するプレートに大きな軸力が作用する。この軸力により発生するプレートの接触面圧が高いほど、スティックスリップ音発生のエネルギーが大きくなることから、プレートによるスティックスリップ音の抑制効果を発揮させることが困難となる。また、大きな軸力の作用により、プレート表面のコーティング層が早期に磨耗し、長期に亘る使用でプレートの破損を引き起こす可能性がある。   However, since both Patent Documents 1 and 2 described above have a structure that secures an axial force by tightening the nut 172 and applies a preload to the bearing portion 170, the inboard of the inner ring 120b of the bearing portion 170 is provided. A large axial force acts on the plate interposed between the opposed surfaces of the side end portion 124 b and the shoulder portion 161 of the outer joint member 162. The higher the contact surface pressure of the plate generated by this axial force, the greater the energy of generating stick-slip noise, making it difficult to exert the effect of suppressing stick-slip noise by the plate. In addition, due to the action of a large axial force, the coating layer on the surface of the plate may be worn out early, and the plate may be damaged after long-term use.

そこで、本発明は前述の問題点に鑑みて提案されたもので、その目的とするところは、プレートの接触面圧を規定することにより、スティックスリップ音の抑制効果を確実に発揮させ得る駆動車輪用軸受装置を提供することにある。   Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to drive wheels that can reliably exert the effect of suppressing stick-slip noise by defining the contact surface pressure of the plate. It is to provide a bearing device for use.

前述の目的を達成するための技術的手段として、本発明は、内周に複列の外側軌道面が形成された外方部材と、一端に車輪取付フランジを有すると共に外周に複列の内側軌道面を有し、ハブ輪と内輪からなる内方部材と、外方部材の外側軌道面と内方部材の内側軌道面との間に介装された複列の転動体とを備え、ハブ輪の軸孔に等速自在継手の外側継手部材から延びるステム部を圧入してスプライン嵌合させた駆動車輪用軸受装置において、外側継手部材の肩部と内方部材の端部との対向面間に、表面コーティングにより所定の摺動特性を有する環状プレートを介在させ、環状プレートの接触面圧を３．０×１０６Ｐａ以下としたことを特徴とする。 As technical means for achieving the above-mentioned object, the present invention includes an outer member having a double-row outer raceway surface formed on the inner periphery, a wheel mounting flange at one end, and a double-row inner track on the outer periphery. A hub ring comprising an inner member comprising a hub ring and an inner ring, and a double row rolling element interposed between the outer raceway surface of the outer member and the inner raceway surface of the inner member. In the drive wheel bearing device in which the stem portion extending from the outer joint member of the constant velocity universal joint is press-fitted into the shaft hole of the constant velocity universal joint and is spline-fitted, the distance between the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member Further, an annular plate having a predetermined sliding characteristic is interposed by surface coating, and the contact surface pressure of the annular plate is set to 3.0 × 10 6 Pa or less.

本発明では、外側継手部材の肩部と内方部材の端部との対向面間に、表面コーティングにより所定の摺動特性を有する環状プレートを介在させたことにより、内方部材を有する軸受部と外側継手部材との間の伝達トルク変動と外側継手部材のねじれが生じても、その軸受部と外側継手部材との間での摩擦抵抗を小さくして積極的な滑りが生じるようにすることで、軸受部と外側継手部材との間で急激な滑りが発生することなく、スティックスリップ音の発生を未然に防止することができる。   In the present invention, a bearing portion having an inner member is provided by interposing an annular plate having a predetermined sliding characteristic by surface coating between opposed surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. Even if the transmission torque fluctuation between the outer joint member and the outer joint member is twisted, the frictional resistance between the bearing portion and the outer joint member is reduced so that positive slip occurs. Thus, it is possible to prevent the occurrence of stick-slip noise without causing a sudden slip between the bearing portion and the outer joint member.

この環状プレートの接触面圧を３．０×１０６Ｐａ以下としたことにより、軸力により発生する環状プレートの接触面圧を適正値とすることで、スティックスリップ音発生のエネルギーを大きくすることなく、環状プレートによるスティックスリップ音の抑制効果を確実に発揮させることが容易となる。また、この適正な接触面圧により、回転トルクが入力されても、コーティング材の早期剥がれや早期磨耗などを未然に防止することができ、コーティング材の機能を十分に発揮させることが容易となる。 By setting the contact surface pressure of the annular plate to 3.0 × 10 6 Pa or less, the contact surface pressure of the annular plate generated by the axial force is set to an appropriate value, thereby increasing the energy of generating stick-slip noise. In addition, it becomes easy to reliably exert the effect of suppressing stick-slip noise by the annular plate. In addition, even when rotational torque is input, the proper contact surface pressure can prevent early peeling or early wear of the coating material, and it is easy to fully exhibit the function of the coating material. .

なお、環状プレートの接触面圧が３．０×１０６Ｐａよりも大きいと、スティックスリップ音発生のエネルギーが大きくなり、環状プレートによるスティックスリップ音の抑制効果を確実に発揮させることが困難となる。また、回転トルクの入力により、コーティング材の早期剥がれや早期磨耗などが発生する可能性があり、コーティング材の機能を十分に発揮させることが困難となる。 When the contact surface pressure of the annular plate is larger than 3.0 × 10 6 Pa, the energy for generating stick-slip noise increases, and it becomes difficult to reliably exert the effect of suppressing stick-slip noise by the annular plate. . Further, the input of the rotational torque may cause early peeling or early wear of the coating material, and it becomes difficult to fully exhibit the function of the coating material.

本発明では、外側継手部材の肩部あるいは内方部材の端部の少なくとも一方の対向面の平面度を０．１以下、かつ、直角度を０．１以下とすることが望ましい。「外側継手部材の肩部あるいは内方部材の端部の少なくとも一方の対向面」とは、外側継手部材の肩部の対向面のみ、内方部材の端部の対向面のみ、外側継手部材の肩部と内方部材の端部の両対向面を含むことを意味する。このようにすれば、環状プレートの接触面が外側継手部材の肩部あるいは内方部材の端部の対向面に偏当りすることがなく、環状プレート表面のコーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果を確実に発揮させることができる。なお、外側継手部材の肩部と内方部材の端部の両対向面の平面度を０．１以下、かつ、直角度を０．１以下とすれば、コーティング層の早期磨耗の抑制効果を大きく発揮させることができる。   In the present invention, it is desirable that the flatness of at least one facing surface of the shoulder portion of the outer joint member or the end portion of the inner member is 0.1 or less and the perpendicularity is 0.1 or less. “At least one facing surface of the shoulder of the outer joint member or the end of the inner member” means only the facing surface of the shoulder of the outer joint member, only the facing surface of the end of the inner member, It means that both opposing surfaces of the shoulder portion and the end portion of the inner member are included. In this way, the contact surface of the annular plate does not strike the opposing surface of the shoulder of the outer joint member or the end of the inner member, and premature wear of the coating layer on the surface of the annular plate can be suppressed. Thus, the effect of suppressing the stick-slip sound can be surely exhibited. In addition, if the flatness of both opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member is 0.1 or less and the perpendicularity is 0.1 or less, the effect of suppressing early wear of the coating layer can be obtained. It can be greatly demonstrated.

ここで、前述の平面度とは、環状プレートと当接する外側継手部材の肩部あるいは内方部材の端部の対向面がどの程度平坦であるかを指標する度合いを意味し、直角度とは、環状プレートと当接する外側継手部材の肩部あるいは内方部材の端部の対向面がジョイント軸芯に対してどの程度直角であるかを指標する度合いを意味する。これら平面度と直角度は、その数値が小さければ小さいほど平坦であり、また、直角であることを示す。   Here, the above-mentioned flatness means a degree indicating how flat the opposing surface of the shoulder portion of the outer joint member that contacts the annular plate or the end portion of the inner member is, and the squareness means It means the degree of indicating how much the opposing surface of the shoulder portion of the outer joint member that contacts the annular plate or the end portion of the inner member is perpendicular to the joint axis. These flatness and perpendicularity indicate that the smaller the numerical value, the flatter and perpendicular.

なお、外側継手部材の肩部あるいは内方部材の端部の対向面の平面度が０．１よりも大きいか、あるいは、直角度が０．１よりも大きいと、環状プレートの接触面が外側継手部材の肩部あるいは内方部材の端部の対向面に偏当りする可能性があり、環状プレート表面のコーティング層の早期磨耗を抑制することが困難となってスティックスリップ音の抑制効果を確実に発揮させることが困難となる。   If the flatness of the opposing surface of the shoulder portion of the outer joint member or the end portion of the inner member is greater than 0.1, or if the squareness is greater than 0.1, the contact surface of the annular plate is outside. There is a possibility of uneven contact with the shoulder surface of the joint member or the end surface of the inner member, which makes it difficult to suppress premature wear of the coating layer on the surface of the annular plate, ensuring the effect of suppressing stick-slip noise. It becomes difficult to make it appear.

本発明は、環状プレートの外径を、外側継手部材の肩部と内方部材の端部の両対向面のうちでその外径が小さい方の部材の外径以下としたことを特徴とする。これにより、環状プレートの外径側部位での変形を防止することができ、また、その環状プレートの接触面が外側継手部材の肩部と内方部材の端部の両対向面に偏当りすることが防止でき、環状プレート表面のコーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果を確実に発揮させることができる。 The present invention is characterized in that the outer diameter of the annular plate is set to be equal to or smaller than the outer diameter of the member having the smaller outer diameter among the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. . This ensures that it is possible to prevent the deformation of the outside diameter side portion of the annular plate, also polarization per the two facing surfaces of the end portion of the shoulder portion and the inner member of the contact surface of the annular plate outer joint member Can be prevented, early wear of the coating layer on the surface of the annular plate can be suppressed, and the effect of suppressing stick-slip noise can be reliably exhibited.

また、本発明は、環状プレートの内径を、外側継手部材の肩部と内方部材の端部の両対向面のうちでその内径が大きい方の部材の内径以上としたことを特徴とする。これにより、環状プレートの内径側部位での変形を防止することができ、また、その環状プレートの接触面が外側継手部材の肩部と内方部材の端部の両対向面に偏当りすることが防止でき、環状プレート表面のコーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果を確実に発揮させることができる。 Further, the present invention is characterized in that the inner diameter of the annular plate is set to be equal to or larger than the inner diameter of the member having the larger inner diameter among the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. This ensures that it is possible to prevent deformation of the inner diameter side portion of the annular plate, also the contact surfaces of the annular plate is polarized per the two facing surfaces of the end portion of the shoulder portion and the inner member of the outer joint member It is possible to prevent this, and early wear of the coating layer on the surface of the annular plate can be suppressed, and the effect of suppressing stick-slip noise can be reliably exhibited.

さらに、本発明は、環状プレートの外径を、外側継手部材の肩部と内方部材の端部の両対向面のうちでその外径が小さい方の部材の外径以下とし、かつ、環状プレートの内径を、外側継手部材の肩部と内方部材の端部の両対向面のうちでその内径が大きい方の部材の内径以上としたことを特徴とする。これにより、環状プレートの外径側と内径側で、つまり、径方向全体に亘って変形を防止することができ、また、その環状プレートの接触面が外側継手部材の肩部と内方部材の端部の両対向面に偏当りすることが防止でき、環状プレート表面のコーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果をより一層確実に発揮させることができる。 Further, according to the present invention, the outer diameter of the annular plate is set to be equal to or smaller than the outer diameter of the member having the smaller outer diameter out of the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. the inner diameter of the plate, characterized in that the outer joint member of the shoulder and the inner member end portion of the above inner diameter towards member an inner diameter greater among the two facing surfaces of the. This ensures that at the outer diameter side and inner diameter side of the annular plate, that is, it is possible to prevent deformation over the entire radial direction, the shoulder portion and the inner member of the contact surface of the annular plate outer joint member It is possible to prevent uneven contact with both opposing surfaces of the end portion of the metal plate, to suppress early wear of the coating layer on the surface of the annular plate, and to more reliably exhibit the effect of suppressing stick-slip noise.

なお、この軸受装置は、ハブ輪の外周面に一対の内輪を嵌合させ、一方の内輪の外周面にアウトボード側の内側軌道面を形成し、他方の内輪の外周面にインボード側の内側軌道面を形成したタイプに適用可能で、この場合、インボード側に位置する他方の内輪のインボード側端部を外側継手部材の肩部と対向させた構造となる。   In this bearing device, a pair of inner rings is fitted to the outer peripheral surface of the hub wheel, an inner raceway surface on the outboard side is formed on the outer peripheral surface of one inner ring, and an inboard side surface is formed on the outer peripheral surface of the other inner ring. The present invention can be applied to a type in which an inner raceway surface is formed. In this case, the inboard side end portion of the other inner ring located on the inboard side is opposed to the shoulder portion of the outer joint member.

また、この軸受装置は、前述したタイプ以外に、一方の内側軌道面が形成されたハブ輪の外周面に小径段部を形成し、その小径段部に他方の内側軌道面が形成された内輪を圧入した上でハブ輪の小径段部の端部を加締めたタイプにも適用可能で、この場合、ハブ輪の加締め部を外側継手部材の肩部と対向させた構造となる。   In addition to the type described above, this bearing device has an inner ring in which a small-diameter step portion is formed on the outer peripheral surface of the hub ring on which one inner raceway surface is formed, and the other inner raceway surface is formed on the small-diameter step portion. Can be applied to a type in which the end of the small-diameter step portion of the hub ring is crimped, and in this case, the structure is such that the crimped portion of the hub ring is opposed to the shoulder portion of the outer joint member.

本発明では、外側継手部材の肩部と内方部材の端部との対向面間に、表面コーティングにより所定の摺動特性を有する環状プレートを介在させた構造としている。これにより、車両発進時、静止状態にある軸受部のハブ輪に対して等速自在継手の外側継手部材から回転トルクが負荷された場合、内方部材を有する軸受部と外側継手部材との間の伝達トルク変動と外側継手部材のねじれが生じても、その軸受部と外側継手部材との間での摩擦抵抗を小さくして積極的な滑りが生じるようにすることで、軸受部と外側継手部材との間で急激な滑りが発生することはない。その結果、スティックスリップ音の発生を未然に防止することができ、静粛性の向上が図れて搭乗者の違和感を解消することができる。   In this invention, it is set as the structure which interposed the annular plate which has a predetermined sliding characteristic by surface coating between the opposing surfaces of the shoulder part of an outer joint member, and the edge part of an inner member. As a result, when a rotational torque is applied from the outer joint member of the constant velocity universal joint to the hub wheel of the bearing portion in a stationary state when the vehicle starts, the space between the bearing portion having the inner member and the outer joint member is reduced. Even if the transmission torque fluctuation of the outer joint member and the outer joint member are twisted, the friction resistance between the bearing portion and the outer joint member is reduced so as to cause positive slipping. No sudden slip occurs between the members. As a result, it is possible to prevent the occurrence of stick-slip noise, improve quietness, and eliminate a sense of discomfort for the passenger.

この環状プレートの接触面圧を３．０×１０６Ｐａ以下としたことにより、軸力により発生する環状プレートの接触面圧を適正値とすることで、スティックスリップ音発生のエネルギーを大きくすることなく、環状プレートによるスティックスリップ音の抑制効果を確実に発揮させることが容易となる。また、この適正な接触面圧により、回転トルクが入力されても、コーティング材の早期剥がれや早期磨耗などを未然に防止することができ、コーティング材の機能を十分に発揮させることが容易となり、耐スティックスリップ性を長期に亘って確保した駆動車輪用軸受装置を提供することができる。 By setting the contact surface pressure of the annular plate to 3.0 × 10 6 Pa or less, the contact surface pressure of the annular plate generated by the axial force is set to an appropriate value, thereby increasing the energy of generating stick-slip noise. In addition, it becomes easy to reliably exert the effect of suppressing stick-slip noise by the annular plate. In addition, with this proper contact surface pressure, even if rotational torque is input, it is possible to prevent early peeling or early wear of the coating material, making it easy to fully demonstrate the function of the coating material, It is possible to provide a drive wheel bearing device in which stick-slip resistance is ensured over a long period of time.

本発明に係る駆動車輪用軸受装置の実施形態を以下に詳述する。図１に示す第一の実施形態の軸受装置は、内方部材であるハブ輪１０および内輪２０ａ，２０ｂ、複列の転動体３０，４０、外方部材である外輪５０、等速自在継手６０を主要な構成要素としている。なお、以下の説明では、車両に組み付けた状態で、車両の外側寄りとなる側をアウトボード側（図面左側）と呼び、中央寄りとなる側をインボード側（図面右側）と呼ぶ。   Embodiments of a drive wheel bearing device according to the present invention will be described in detail below. The bearing device of the first embodiment shown in FIG. 1 includes a hub ring 10 and inner rings 20a and 20b that are inner members, double-row rolling elements 30 and 40, an outer ring 50 that is an outer member, and a constant velocity universal joint 60. Is the main component. In the following description, the side closer to the outside of the vehicle in the state assembled to the vehicle is referred to as the outboard side (left side in the drawing), and the side closer to the center is referred to as the inboard side (right side in the drawing).

ハブ輪１０は、そのアウトボード側の端部に、車輪（図示せず）を取り付けるための車輪取付フランジ１４を備えている。この車輪取付フランジ１４の円周方向等間隔に、ホイールディスクを固定するためのハブボルト１６が植設されている。   The hub wheel 10 includes a wheel mounting flange 14 for mounting a wheel (not shown) at an end portion on the outboard side. Hub bolts 16 for fixing the wheel disc are implanted at equal intervals in the circumferential direction of the wheel mounting flange 14.

このハブ輪１０の外周面に一対の内輪２０ａ，２０ｂを嵌合させ、アウトボード側に位置する一方の内輪２０ａの外周面にアウトボード側の内側軌道面２２ａが形成され、インボード側に位置する他方の内輪２０ｂの外周面にインボード側の内側軌道面２２ｂが形成されている。これらアウトボード側の内側軌道面２２ａとインボード側の内側軌道面２２ｂとで複列の内側軌道面を構成している。このハブ輪１０の軸孔の内周面には、等速自在継手６０をトルク伝達可能に連結するための雌スプライン１１が形成されている。   A pair of inner rings 20a and 20b are fitted to the outer peripheral surface of the hub wheel 10, and an inner raceway surface 22a on the outboard side is formed on the outer peripheral surface of one inner ring 20a located on the outboard side, and is positioned on the inboard side. An inner raceway surface 22b on the inboard side is formed on the outer peripheral surface of the other inner ring 20b. These outboard side inner raceway surface 22a and inboard side inner raceway surface 22b constitute a double row inner raceway surface. A female spline 11 for connecting the constant velocity universal joint 60 so as to transmit torque is formed on the inner peripheral surface of the shaft hole of the hub wheel 10.

外輪５０は、内周面に内輪２０ａ，２０ｂの内側軌道面２２ａ，２２ｂと対向する複列の外側軌道面５２，５４が形成され、車体（図示せず）に取り付けるための車体取付フランジ５６を備えている。この車体取付フランジ５６は、車体の懸架装置（図示せず）から延びるナックルに取り付け孔５８を利用してボルト等で固定される。   The outer ring 50 is formed with double row outer raceway surfaces 52 and 54 facing the inner raceway surfaces 22a and 22b of the inner races 20a and 20b on the inner peripheral surface, and a vehicle body attachment flange 56 for attaching to a vehicle body (not shown). I have. The vehicle body attachment flange 56 is fixed to a knuckle extending from a suspension device (not shown) of the vehicle body with a bolt or the like using an attachment hole 58.

軸受部７０は、複列のアンギュラ玉軸受構造で、内輪２０ａ，２０ｂの外周面に形成された内側軌道面２２ａ，２２ｂと外輪５０の内周面に形成された外側軌道面５２，５４との間に転動体３０，４０を介在させ、各列の転動体３０，４０を保持器３２，４２により円周方向等間隔に回転自在に保持した構造を有する。   The bearing portion 70 has a double-row angular contact ball bearing structure, and includes inner raceway surfaces 22a and 22b formed on the outer peripheral surfaces of the inner rings 20a and 20b and outer raceway surfaces 52 and 54 formed on the inner peripheral surface of the outer ring 50. The rolling elements 30 and 40 are interposed therebetween, and the rolling elements 30 and 40 in each row are held by the cages 32 and 42 so as to be rotatable at equal intervals in the circumferential direction.

軸受部７０の両端開口部には、内輪２０ａ，２０ｂの外周面に摺接するように、外輪５０と内輪２０ａ，２０ｂとの環状空間を密封する一対のシール３４，４４が外輪５０の両端部内径に嵌合され、内部に充填されたグリースの漏洩ならびに外部からの水や異物の侵入を防止するようになっている。   A pair of seals 34, 44 that seal the annular space between the outer ring 50 and the inner rings 20 a, 20 b so as to be in sliding contact with the outer peripheral surfaces of the inner rings 20 a, 20 b are formed at both end openings of the bearing part 70. And prevents leakage of grease filled in the inside and intrusion of water and foreign matters from the outside.

前述したハブ輪１０に等速自在継手６０の外側継手部材６２を連結することにより、軸受装置が構成される。等速自在継手６０の外側継手部材６２は、ドライブシャフトを構成する中間軸（図示せず）の一端に設けられ、内側継手部材、ボールおよびケージからなる内部部品（図示せず）を収容したカップ状のマウス部６４と、そのマウス部６４の基部から軸方向に一体に延びるステム部６６とで構成されている。このステム部６６の外周面には、前述のハブ輪１０をトルク伝達可能に連結するための雄スプライン６８が形成されている。   A bearing device is configured by connecting the outer joint member 62 of the constant velocity universal joint 60 to the hub wheel 10 described above. The outer joint member 62 of the constant velocity universal joint 60 is provided at one end of an intermediate shaft (not shown) constituting the drive shaft, and accommodates an internal part (not shown) composed of an inner joint member, a ball and a cage. And a stem portion 66 integrally extending in the axial direction from the base portion of the mouse portion 64. On the outer peripheral surface of the stem portion 66, a male spline 68 for connecting the hub wheel 10 described above so as to transmit torque is formed.

この外側継手部材６２のステム部６６をハブ輪１０の軸孔に圧入し、ステム部６６の外周面に形成された雄スプライン６８とハブ輪１０の軸孔内周面に形成された雌スプライン１１を嵌合させることにより、トルク伝達可能となっている。この実施形態の軸受装置においては、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂとの対向面間に所定の摺動特性を有する環状プレート８０ａを介在させ、ステム部６６の端部に形成された雄ねじ部６５にナット７２を締め付けることによって、等速自在継手６０をハブ輪１０に固定すると共にそのナット７２による締め付け力（軸力）でもって軸受部７０に予圧を付与している。なお、等速自在継手６０とハブ輪１０は、前述のナット７２以外に、ボルトにより固定することも可能である。   The stem portion 66 of the outer joint member 62 is press-fitted into the shaft hole of the hub wheel 10, and the male spline 68 formed on the outer peripheral surface of the stem portion 66 and the female spline 11 formed on the inner peripheral surface of the shaft ring of the hub wheel 10. The torque can be transmitted by fitting. In the bearing device of this embodiment, an annular plate 80a having a predetermined sliding characteristic is interposed between the opposed surfaces of the shoulder portion 61 of the outer joint member 62 and the inboard side end portion 24b of the inner ring 20b, and the stem portion 66 is interposed. The constant velocity universal joint 60 is fixed to the hub wheel 10 by tightening the nut 72 to the male thread portion 65 formed at the end of the shaft, and a preload is applied to the bearing portion 70 by the tightening force (axial force) by the nut 72. doing. The constant velocity universal joint 60 and the hub wheel 10 can be fixed by bolts in addition to the nut 72 described above.

ナット７２による所定の締付力（軸力）でもって、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂとの対向面間に環状プレート８０ａを挟み込んだ構造としている。外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂとの対向面間に介在された環状プレート８０ａは、例えば、二硫化モリブデン系あるいはフッ素樹脂系などのコーティング材による皮膜で表面コーティングすることにより所定の摺動特性を有する。また、この環状プレート８０ａの接触面圧を３．０×１０６Ｐａ以下とする。この環状プレート８０ａの接触面圧は小さいほどよく、例えば１．８×１０６Ｐａが好ましい。 An annular plate 80a is sandwiched between opposed surfaces of the shoulder 61 of the outer joint member 62 and the inboard side end 24b of the inner ring 20b with a predetermined tightening force (axial force) by the nut 72. The annular plate 80a interposed between the opposing surfaces of the shoulder 61 of the outer joint member 62 and the inboard side end 24b of the inner ring 20b is a surface with a coating of a coating material such as molybdenum disulfide or fluororesin. By coating, it has a predetermined sliding characteristic. Further, the contact surface pressure of the annular plate 80a is set to 3.0 × 10 6 Pa or less. The contact surface pressure of the annular plate 80a is preferably as small as possible. For example, 1.8 × 10 6 Pa is preferable.

このように、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂとの対向面間に、表面コーティングにより摺動特性の優れた環状プレート８０ａを介在させたことにより、軸受部７０と外側継手部材６２との間の伝達トルク変動と外側継手部材６２のねじれが生じても、その軸受部７０と外側継手部材６２との間での摩擦抵抗を小さくして積極的な滑りが生じるようにすることで、軸受部７０と外側継手部材６２との間で急激な滑りが発生することなく、スティックスリップ音の発生を未然に防止することができる。   As described above, the annular plate 80a having excellent sliding characteristics is provided by the surface coating between the facing surfaces of the shoulder 61 of the outer joint member 62 and the inboard side end 24b of the inner ring 20b. Even if transmission torque fluctuations between the outer joint member 62 and the outer joint member 62 are torsioned, the frictional resistance between the bearing portion 70 and the outer joint member 62 is reduced, and positive slipping occurs. By making it generate | occur | produce, generation | occurrence | production of a stick slip sound can be prevented beforehand, without generate | occur | producing a sudden slip between the bearing part 70 and the outer joint member 62. FIG.

この環状プレート８０ａの接触面圧を３．０×１０６Ｐａ以下としたことにより、軸力により発生する環状プレート８０ａの接触面圧を適正値とすることで、スティックスリップ音発生のエネルギーを大きくすることなく、環状プレート８０ａによるスティックスリップ音の抑制効果を確実に発揮させることが容易となる。また、この適正な接触面圧により、回転トルクが入力されても、コーティング材の早期剥がれや早期磨耗などを未然に防止することができ、コーティング材の機能を十分に発揮させることが容易となる。 By setting the contact surface pressure of the annular plate 80a to 3.0 × 10 6 Pa or less, the contact surface pressure of the annular plate 80a generated by the axial force is set to an appropriate value, thereby increasing the energy of generating stick-slip noise. Without this, it becomes easy to reliably exert the effect of suppressing stick-slip noise by the annular plate 80a. In addition, even when rotational torque is input, the proper contact surface pressure can prevent early peeling or early wear of the coating material, and it is easy to fully exhibit the function of the coating material. .

なお、環状プレート８０ａの接触面圧が３．０×１０６Ｐａよりも大きいと、スティックスリップ音発生のエネルギーが大きくなり、環状プレート８０ａによるスティックスリップ音の抑制効果を確実に発揮させることが困難となる。また、回転トルクの入力により、コーティング材の早期剥がれや早期磨耗などが発生する可能性があり、コーティング材の機能を十分に発揮させることが困難となる。 If the contact surface pressure of the annular plate 80a is larger than 3.0 × 10 6 Pa, the energy of generating stick-slip noise increases, and it is difficult to reliably exert the effect of suppressing stick-slip noise by the annular plate 80a. It becomes. Further, the input of the rotational torque may cause early peeling or early wear of the coating material, and it becomes difficult to fully exhibit the function of the coating material.

本出願人が実施した試験によると、コーティング材が二硫化モリブデン系の場合、環状プレート８０ａの接触面圧を３．０×１０６Ｐａに設定すると、内輪２０ｂのインボード側端部２４ｂと外側継手部材６２の肩部６１との間で急激な滑りは発生したが、スティックスリップ音は発生しなかった。この環状プレート８０ａの接触面圧を１．８×１０６Ｐａに設定すると、内輪２０ｂのインボード側端部２４ｂと外側継手部材６２の肩部６１との間で急激な滑りが発生せず、スティックスリップ音も発生しなかった。 According to a test conducted by the present applicant, when the coating material is molybdenum disulfide, and the contact surface pressure of the annular plate 80a is set to 3.0 × 10 6 Pa, the inner end 20b of the inner ring 20b and the outer side A sudden slip occurred between the joint 61 and the shoulder 61, but no stick-slip noise was generated. When the contact surface pressure of the annular plate 80a is set to 1.8 × 10 6 Pa, a sudden slip does not occur between the inboard side end portion 24b of the inner ring 20b and the shoulder portion 61 of the outer joint member 62, There was no stick-slip noise.

また、コーティング材がフッ素樹脂系の場合、環状プレート８０ａの接触面圧を３．０×１０６Ｐａあるいは１．８×１０６Ｐａのいずれに設定しても、内輪２０ｂのインボード側端部２４ｂと外側継手部材６２の肩部６１との間で急激な滑りが発生せず、スティックスリップ音も発生しなかった。 Further, when the coating material is a fluororesin system, the inboard side end portion of the inner ring 20b is set regardless of whether the contact surface pressure of the annular plate 80a is set to 3.0 × 10 6 Pa or 1.8 × 10 6 Pa. No sudden slip occurred between 24b and the shoulder 61 of the outer joint member 62, and no stick-slip sound was generated.

以上で説明した第一の実施形態では、ハブ輪１０の外周面に一対の内輪２０ａ，２０ｂを嵌合させ、インボード側に位置する他方の内輪２０ｂのインボード側端部２４ｂを外側継手部材６２の肩部６１に対向させたタイプの軸受装置に適用した場合について説明したが、本発明はこれに限定されることはない。   In the first embodiment described above, the pair of inner rings 20a and 20b are fitted to the outer peripheral surface of the hub wheel 10, and the inboard side end 24b of the other inner ring 20b located on the inboard side is connected to the outer joint member. Although the case where the present invention is applied to a bearing device of the type opposed to the shoulder portion 61 of 62 has been described, the present invention is not limited to this.

例えば、図２に示すように、一方の内側軌道面１２が形成されたハブ輪１０の外周面に小径段部１８を形成し、その小径段部１８に他方の内側軌道面２２が形成された内輪２０を圧入した上でハブ輪１０の小径段部１８の端部を加締め、その加締め部１３を外側継手部材６２の肩部６１に対向させたタイプの軸受装置にも適用可能である。   For example, as shown in FIG. 2, a small diameter step portion 18 is formed on the outer peripheral surface of the hub wheel 10 on which one inner raceway surface 12 is formed, and the other inner raceway surface 22 is formed on the small diameter step portion 18. The present invention is also applicable to a type of bearing device in which the inner ring 20 is press-fitted and the end portion of the small-diameter step portion 18 of the hub wheel 10 is swaged and the swaged portion 13 is opposed to the shoulder portion 61 of the outer joint member 62. .

このタイプの軸受装置では、ハブ輪１０の外周面に形成されたアウトボード側の内側軌道面１２と、内輪２０の外周面に形成されたインボード側の内側軌道面２２とで複列の内側軌道面を構成している。この内輪２０をハブ輪１０の小径段部１８に圧入し、ハブ輪１０の小径段部１８の端部を外側に加締めることにより、その加締め部１３でもって内輪２０を抜け止めしてハブ輪１０と一体化し、軸受部７０に予圧を付与している。   In this type of bearing device, the inner raceway 12 on the outboard side formed on the outer peripheral surface of the hub wheel 10 and the inner raceway surface 22 on the inboard side formed on the outer peripheral surface of the inner ring 20 are arranged in a double row. It constitutes the raceway surface. The inner ring 20 is press-fitted into the small-diameter step portion 18 of the hub wheel 10, and the end portion of the small-diameter step portion 18 of the hub wheel 10 is crimped to the outside, so that the inner ring 20 is prevented from being detached by the crimping portion 13. The bearing 10 is integrated with the wheel 10 to apply a preload.

図１に示す第一の実施形態では、内輪２０ｂのインボード側端部２４ｂを外側継手部材６２の肩部６１に対向させ、環状プレート８０ａを内輪２０ｂのインボード側端部２４ｂと外側継手部材６２の肩部６１との対向面間に介在させた構造としている。一方、図２に示す第二の実施形態では、ハブ輪１０の小径段部１８の加締め部１３を外側継手部材６２の肩部６１と対向させ、環状プレート８０ｂをハブ輪１０の加締め部１３と外側継手部材６２の肩部６１との対向面間に介在させた構造となっている。   In the first embodiment shown in FIG. 1, the inboard side end 24b of the inner ring 20b is opposed to the shoulder 61 of the outer joint member 62, and the annular plate 80a is connected to the inboard side end 24b of the inner ring 20b and the outer joint member. The structure is interposed between the opposing surfaces of the shoulder portions 61 of the 62. On the other hand, in the second embodiment shown in FIG. 2, the caulking portion 13 of the small-diameter step portion 18 of the hub wheel 10 is opposed to the shoulder portion 61 of the outer joint member 62, and the annular plate 80 b is moved to the caulking portion of the hub wheel 10. 13 and the shoulder 61 of the outer joint member 62.

この第二の実施形態でも、第一の実施形態と同様、ステム部６６の端部に形成された雄ねじ部６５にナット７２を締め付けることによって、等速自在継手６０をハブ輪１０に固定し、そのナット７２による所定の締付力（軸力）でもって、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３との対向面間に環状プレート８０ｂを挟み込んだ構造としている。なお、表面コーティングにより所定の摺動特性を有する環状プレート８０ｂの接触面圧を３．０×１０６Ｐａ以下（好ましくは、１．８×１０６Ｐａ）とする点、およびそれらの作用効果については、第一の実施形態と同様であるため、重複説明は省略する。 In the second embodiment, as in the first embodiment, the constant velocity universal joint 60 is fixed to the hub wheel 10 by tightening the nut 72 to the male screw portion 65 formed at the end portion of the stem portion 66. An annular plate 80b is sandwiched between opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the caulking portion 13 of the hub wheel 10 with a predetermined tightening force (axial force) by the nut 72. In addition, about the point which makes the contact surface pressure of the annular plate 80b which has a predetermined sliding characteristic by surface coating 3.0 * 10 < 6 > Pa or less (preferably 1.8 * 10 < 6 > Pa), and those effects Since this is the same as that of the first embodiment, redundant description is omitted.

図１に示す第一の実施形態および図２に示す第二の実施形態の軸受装置において、外側継手部材６２の肩部６１の対向面の平面度を０．１以下、かつ、直角度を０．１以下とする。好ましくは、平面度を０．０５以下、かつ、直角度を０．０５以下とすればよい。ここで、平面度とは、環状プレート８０ａ，８０ｂと当接する外側継手部材６２の肩部６１の対向面がどの程度平坦であるかを指標する度合いを意味し、直角度とは、環状プレート８０ａ，８０ｂと当接する外側継手部材６２の肩部６１の対向面がジョイント軸芯に対してどの程度直角であるかを指標する度合いを意味する。これら平面度と直角度は、その数値が小さければ小さいほど平坦であり、また、直角であることを示す。   In the bearing device of the first embodiment shown in FIG. 1 and the second embodiment shown in FIG. 2, the flatness of the facing surface of the shoulder portion 61 of the outer joint member 62 is 0.1 or less, and the perpendicularity is 0. .1 or less. Preferably, the flatness may be 0.05 or less and the perpendicularity may be 0.05 or less. Here, the flatness means a degree indicating how flat the opposing surface of the shoulder portion 61 of the outer joint member 62 contacting the annular plates 80a and 80b is, and the squareness means the annular plate 80a. , 80b, the degree to which the opposite surface of the shoulder portion 61 of the outer joint member 62 abuts against the joint axis is indicated. These flatness and perpendicularity indicate that the smaller the numerical value, the flatter and perpendicular.

このように、外側継手部材６２の肩部６１の対向面の平面度を０．１以下、かつ、直角度を０．１以下としたことにより、環状プレート８０ａ，８０ｂの接触面が外側継手部材６２の肩部６１の対向面に偏当りすることがなく、環状プレート８０ａ，８０ｂの表面コーティング層が早期に磨耗することを抑制できてスティックスリップ音の抑制効果を確実に発揮させることができる。   Thus, the flatness of the opposing surface of the shoulder portion 61 of the outer joint member 62 is 0.1 or less and the perpendicularity is 0.1 or less, so that the contact surfaces of the annular plates 80a and 80b are the outer joint members. Therefore, the surface coating layer of the annular plates 80a and 80b can be prevented from being worn out at an early stage, and the effect of suppressing stick-slip noise can be reliably exhibited.

なお、外側継手部材６２の肩部６１の対向面の平面度が０．１よりも大きいか、あるいは、直角度が０．１よりも大きいと、環状プレート８０ａ，８０ｂの接触面が外側継手部材６２の肩部６１の対向面に偏当りする可能性があり、環状プレート８０ａ，８０ｂの表面コーティング層の早期磨耗を抑制することが困難となってスティックスリップ音の抑制効果を確実に発揮させることが困難となる。   When the flatness of the opposing surface of the shoulder portion 61 of the outer joint member 62 is greater than 0.1 or the squareness is greater than 0.1, the contact surfaces of the annular plates 80a, 80b are the outer joint members. 62 is likely to be offset against the opposing surface of the shoulder portion 61 of the shoulder 62, and it is difficult to suppress early wear of the surface coating layer of the annular plates 80a and 80b, so that the effect of suppressing stick-slip noise can be reliably exhibited. It becomes difficult.

なお、前述の実施形態では、外側継手部材６２の肩部６１の対向面の平面度を０．１以下、かつ、直角度を０．１以下とした場合について説明したが、図１に示す第一の実施形態であれば、内輪２０ｂのインボード側端部２４ｂの対向面の平面度を０．１以下、かつ、直角度を０．１以下としてもよい。また、図２に示す第二の実施形態であれば、ハブ輪１０の加締め部１３との対向面の平面度を０．１以下、かつ、直角度を０．１以下としてもよい。このとき、内輪２０ｂのインボード側端部２４ｂあるいはハブ輪１０の加締め部１３の対向面の平面度を０．１以下、かつ、直角度を０．１以下とした作用効果については、外側継手部材６２の肩部６１の対向面の平面度を０．１以下、かつ、直角度を０．１以下とした場合と同様であるため、重複説明は省略する。   In the above-described embodiment, the case where the flatness of the facing surface of the shoulder 61 of the outer joint member 62 is 0.1 or less and the perpendicularity is 0.1 or less has been described. In one embodiment, the flatness of the facing surface of the inboard side end 24b of the inner ring 20b may be 0.1 or less, and the squareness may be 0.1 or less. In the second embodiment shown in FIG. 2, the flatness of the surface of the hub wheel 10 facing the caulking portion 13 may be 0.1 or less and the squareness may be 0.1 or less. At this time, the effect of setting the flatness of the opposing surface of the inboard side end portion 24b of the inner ring 20b or the crimped portion 13 of the hub ring 10 to 0.1 or less and the perpendicularity to 0.1 or less Since the flatness of the opposing surface of the shoulder portion 61 of the joint member 62 is 0.1 or less and the perpendicularity is 0.1 or less, duplicate description is omitted.

さらに、外側継手部材６２の肩部６１の対向面と、内輪２０ｂのインボード側端部２４ｂあるいはハブ輪１０の加締め部１３の対向面の両方の平面度を０．１以下、かつ、直角度を０．１以下としてもよい。このようにすれば、環状プレート８０ａ，８０ｂの表面コーティング層が早期に磨耗することをより一層抑制できてスティックスリップ音の抑制効果をより一層確実に発揮させることができる。   Further, the flatness of both the facing surface of the shoulder portion 61 of the outer joint member 62 and the facing surface of the inboard side end portion 24b of the inner ring 20b or the caulking portion 13 of the hub wheel 10 is 0.1 or less, and The angle may be 0.1 or less. In this way, it is possible to further prevent the surface coating layers of the annular plates 80a and 80b from being worn out at an early stage, and to more reliably exhibit the effect of suppressing stick-slip noise.

図３は、図１に示す第一の実施形態の軸受装置において、環状プレート８０ａ１の外径を、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂの両対向面のうちでその外径が小さい方の部材、つまり、外側継手部材６２の肩部６１の対向面の外径以下とした構造を例示する。図３に示す第三の実施形態では、環状プレート８０ａ１の外径を外側継手部材６２の肩部６１の対向面の外径と一致させ、環状プレート８０ａ１の内径を外側継手部材６２の肩部６１の対向面の内径と一致させている。なお、図中、Ｘ１は外側継手部材６２の肩部６１の対向面（平坦面）の径方向寸法、Ｙ１は内輪２０ｂのインボード側端部２４ｂの対向面（平坦面）の径方向寸法をそれぞれ示す。 3, the bearing apparatus of the first embodiment shown in FIG. 1, the outer diameter of the annular plate 80a 1, the inboard-side end portion 24b of the shoulder portion 61 and the inner ring 20b of the outer joint member 62 of the two facing surfaces A member having a smaller outer diameter, that is, a structure in which the outer diameter of the opposing surface of the shoulder portion 61 of the outer joint member 62 is equal to or smaller than that is illustrated. In a third embodiment shown in FIG. 3, to match the outer diameter of the opposing surfaces of the shoulder portion 61 of the outer joint member 62 to the outer diameter of the annular plate 80a 1, the inner diameter of the annular plate 80a 1 of the outer joint member 62 shoulder It is made to correspond with the internal diameter of the opposing surface of the part 61. FIG. In the figure, X 1 is a radial direction of the radial dimension of the facing surface of the shoulder portion 61 of the outer joint member 62 (flat surface), Y 1 is the facing surface of the inboard-side end portion 24b of the inner ring 20b (flat surface) Each dimension is shown.

図４は、図２に示す第二の実施形態の軸受装置において、環状プレート８０ｂ１の外径を、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３の両対向面のうちでその外径が小さい方の部材、つまり、ハブ輪１０の加締め部１３の対向面の外径以下とした構造を例示する。図４に示す第四の実施形態では、環状プレート８０ｂ１の外径をハブ輪１０の加締め部１３の対向面の外径と一致させ、環状プレート８０ｂ１の内径を外側継手部材６２の肩部６１の対向面の内径と一致させている。なお、図中、Ｘ２は外側継手部材６２の肩部６１の対向面（平坦面）の径方向寸法、Ｙ２はハブ輪１０の加締め部１３の対向面（平坦面）の径方向寸法をそれぞれ示す。 FIG. 4 shows the bearing device of the second embodiment shown in FIG. 2, wherein the outer diameter of the annular plate 80 b 1 is determined from the opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the caulking portion 13 of the hub wheel 10. Then, a member having a smaller outer diameter, that is, a structure in which the outer diameter of the facing surface of the caulking portion 13 of the hub wheel 10 is equal to or smaller than that is illustrated. In the fourth embodiment shown in FIG. 4, the outer diameter of the annular plate 80b 1 to match the outer diameter of the opposed surfaces of the crimped portion 13 of the hub wheel 10, the inner diameter of the annular plate 80b 1 of the outer joint member 62 shoulder It is made to correspond with the internal diameter of the opposing surface of the part 61. FIG. Note that the radial dimension in Fig, X 2 is the radial dimension of the opposing surface of the shoulder portion 61 of the outer joint member 62 (flat surface), Y 2 is the facing surface of the crimped portion 13 of the hub wheel 10 (flat surface) Respectively.

これら第三の実施形態および第四の実施形態では、環状プレート８０ａ１，８０ｂ１の外径側部位での変形を防止することができ、また、その環状プレート８０ａ１，８０ｂ１の接触面が外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂあるいは加締め部１３の両対向面に偏当りすることが防止でき、環状プレート８０ａ１，８０ｂ１の表面コーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果を確実に発揮させることができる。 In the third and fourth embodiments, deformation of the annular plates 80a 1 and 80b 1 at the outer diameter side portion can be prevented, and the contact surfaces of the annular plates 80a 1 and 80b 1 are Premature wear of the surface coating layers of the annular plates 80a 1 , 80b 1 can be prevented from being offset against both the shoulder 61 of the outer joint member 62 and the inboard side end 24b of the inner ring 20b or the opposing surfaces of the crimped portion 13. Can be suppressed, and the effect of suppressing stick-slip noise can be reliably exhibited.

図５は、図１に示す第一の実施形態の軸受装置において、環状プレート８０ａ２の内径を、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂの両対向面のうちでその内径が大きい方の部材、つまり、内輪２０ｂのインボード側端部２４ｂの対向面の内径以上とした構造を例示する。図５に示す第五の実施形態では、環状プレート８０ａ２の内径を内輪２０ｂのインボード側端部２４ｂの内径と一致させ、環状プレート８０ａ２の外径を外側継手部材６２の肩部６１の対向面の外径と一致させている。なお、図中、Ｘ３は外側継手部材６２の肩部６１の対向面（平坦面）の径方向寸法、Ｙ３は内輪２０ｂのインボード側端部２４ｂの対向面（平坦面）の径方向寸法をそれぞれ示す。 5, the bearing device of the first embodiment shown in FIG. 1, the inner diameter of the annular plate 80a 2, of the two facing surfaces of the inboard-side end portion 24b of the shoulder portion 61 and the inner ring 20b of the outer joint member 62 A structure having a larger inner diameter than the inner diameter of the opposing surface of the inner ring 20b, that is, the inboard side end 24b of the inner ring 20b is illustrated. In the fifth embodiment shown in FIG. 5, the inner diameter of the annular plate 80 a 2 is matched with the inner diameter of the inboard side end 24 b of the inner ring 20 b, and the outer diameter of the annular plate 80 a 2 is set to the shoulder 61 of the outer joint member 62. It matches with the outer diameter of the opposing surface. In the figure, X 3 is a radial direction of the radial dimension of the facing surface of the shoulder portion 61 of the outer joint member 62 (flat surface), Y 3 is facing surfaces of the inboard-side end portion 24b of the inner ring 20b (flat surface) Each dimension is shown.

図６は、図２に示す第二の実施形態の軸受装置において、環状プレート８０ｂ２の内径を、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３の両対向面のうちでその内径が大きい方の部材、つまり、ハブ輪１０の加締め部１３の対向面の内径以上とした構造を例示する。図６に示す第六の実施形態では、環状プレート８０ｂ２の内径をハブ輪１０の加締め部１３の対向面の内径と一致させ、環状プレート８０ｂ２の外径を外側継手部材６２の肩部６１の対向面の外径と一致させている。なお、図中、Ｘ４は外側継手部材６２の肩部６１の対向面（平坦面）の径方向寸法、Ｙ４はハブ輪１０の加締め部１３の対向面（平坦面）の径方向寸法をそれぞれ示す。 FIG. 6 shows the bearing device of the second embodiment shown in FIG. 2, wherein the inner diameter of the annular plate 80 b 2 is set between the opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the caulking portion 13 of the hub wheel 10. A member having a larger inner diameter, that is, a structure that is equal to or larger than the inner diameter of the facing surface of the caulking portion 13 of the hub wheel 10 is illustrated. In a sixth embodiment shown in FIG. 6, the inner diameter of the annular plate 80b 2 to match the inner diameter of the opposing surfaces of the crimped portion 13 of the hub wheel 10, the shoulder portion of the outer joint member 62 to the outer diameter of the annular plate 80b 2 It is made to correspond with the outer diameter of 61 opposing surfaces. Note that the radial dimension in Fig, X 4 is the radial dimension of the opposing surface of the shoulder portion 61 of the outer joint member 62 (flat surface), Y 4 is opposed surfaces of the crimped portion 13 of the hub wheel 10 (flat surface) Respectively.

これら第五の実施形態および第六の実施形態では、環状プレート８０ａ２，８０ｂ２の内径側部位での変形を防止することができ、また、その環状プレート８０ａ２，８０ｂ２の接触面が外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂあるいはハブ輪１０の加締め部１３の両対向面に偏当りすることが防止でき、環状プレート８０ａ２，８０ｂ２の表面コーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果を確実に発揮させることができる。 In the fifth and sixth embodiments, deformation of the annular plates 80a 2 and 80b 2 at the inner diameter side portion can be prevented, and the contact surfaces of the annular plates 80a 2 and 80b 2 are outside. It is possible to prevent uneven contact between the shoulder portion 61 of the joint member 62 and the inboard side end portion 24b of the inner ring 20b or the crimping portion 13 of the hub ring 10, and the surface coating layers of the annular plates 80a 2 and 80b 2 Thus, it is possible to suppress the early wear of the stick-slip sound and to reliably exhibit the effect of suppressing stick-slip noise.

図７は、図１に示す第一の実施形態の軸受装置において、環状プレート８０ａ３の外径を、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂの両対向面のうちでその外径が小さい方の部材、つまり、外側継手部材６２の肩部６１の対向面の外径以下とし、かつ、環状プレート８０ａ３の内径を、外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂの両対向面のうちでその内径が大きい方の部材、つまり、内輪２０ｂのインボード側端部２４ｂの対向面の内径以上とした構造を例示する。図７に示す第七の実施形態では、環状プレート８０ａ３の外径を外側継手部材６２の肩部６１の対向面の外径と一致させ、環状プレート８０ａ３の内径を内輪２０ｂのインボード側端部２４ｂの対向面の内径と一致させている。なお、図中、Ｘ５は外側継手部材６２の肩部６１の対向面（平坦面）の径方向寸法、Ｙ５は内輪２０ｂのインボード側端部２４ｂの対向面（平坦面）の径方向寸法をそれぞれ示す。 7, the bearing device of the first embodiment shown in FIG. 1, the outer diameter of the annular plate 80a 3, the inboard-side end portion 24b of the shoulder portion 61 and the inner ring 20b of the outer joint member 62 of the two facing surfaces Among them, the member having the smaller outer diameter, that is, the outer diameter of the opposing surface of the shoulder portion 61 of the outer joint member 62 and the inner diameter of the annular plate 80a 3 are set to the shoulder portion 61 of the outer joint member 62 and the inner ring. A member having a larger inner diameter among the opposing surfaces of the inboard side end portion 24b of 20b, that is, a structure having an inner diameter equal to or larger than the inner diameter of the opposing surface of the inboard side end portion 24b of the inner ring 20b is illustrated. In a seventh embodiment shown in FIG. 7, to match the outer diameter of the opposing surfaces of the shoulder portion 61 of the outer joint member 62 to the outer diameter of the annular plate 80a 3, the inboard side of the inner ring 20b of the inner diameter of the annular plate 80a 3 It is made to correspond with the internal diameter of the opposing surface of the edge part 24b. In the figure, X 5 is radial radial dimension of the facing surface of the shoulder portion 61 of the outer joint member 62 (flat surface), Y 5 is facing surfaces of the inboard-side end portion 24b of the inner ring 20b (flat surface) Each dimension is shown.

図８は、図２に示す第二の実施形態の軸受装置において、環状プレート８０ｂ３の外径を、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３の両対向面のうちでその外径が小さい方の部材、つまり、ハブ輪１０の加締め部１３の対向面の外径以下とし、かつ、環状プレート８０ｂ３の内径を、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３の両対向面のうちでその内径が大きい方の部材、つまり、ハブ輪１０の加締め部１３の対向面の内径以上とした構造を例示する。図８に示す第八の実施形態では、環状プレート８０ｂ３の外径をハブ輪１０の加締め部１３の対向面の外径と一致させ、環状プレート８０ｂ３の内径をハブ輪１０の加締め部１３の対向面の内径と一致させている。なお、図中、Ｘ６は外側継手部材６２の肩部６１の対向面（平坦面）の径方向寸法、Ｙ６はハブ輪１０の加締め部１３の対向面（平坦面）の径方向寸法をそれぞれ示す。 FIG. 8 shows the bearing device according to the second embodiment shown in FIG. 2, wherein the outer diameter of the annular plate 80 b 3 is determined from the opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the caulking portion 13 of the hub wheel 10. in towards member the outer diameter is small, that is, the outer diameter or less of a facing surface of the crimped portion 13 of the hub wheel 10 and the inner diameter of the annular plate 80b 3, shoulder 61 and the hub wheel of the outer joint member 62 10 illustrates a structure in which the inner diameter is larger than the inner diameter of the opposing surface of the caulking portion 13 of the hub wheel 10 among the opposing surfaces of the ten caulking portion 13. In an eighth embodiment of FIG 8, the outer diameter of the annular plate 80b 3 to match the outer diameter of the opposed surfaces of the crimped portion 13 of the hub wheel 10, the caulking of the wheel hub 10 to the inner diameter of the annular plate 80b 3 It is made to correspond with the internal diameter of the opposing surface of the part 13. FIG. In the figure, X 6 is the radial dimension of the opposing surface (flat surface) of the shoulder 61 of the outer joint member 62, and Y 6 is the radial dimension of the opposing surface (flat surface) of the caulking portion 13 of the hub wheel 10. Respectively.

これら第七の実施形態および第八の実施形態では、環状プレート８０ａ３，８０ｂ３の外径側と内径側で、つまり、径方向全体に亘って変形を防止することができ、また、その環状プレート８０ａ３，８０ｂ３の接触面が外側継手部材６２の肩部６１と内輪２０ｂのインボード側端部２４ｂあるいはハブ輪１０の加締め部１３の両対向面に偏当りすることが防止でき、環状プレート８０ａ３，８０ｂ３の表面コーティング層の早期磨耗を抑制することができてスティックスリップ音の抑制効果をより一層確実に発揮させることができる。 In the seventh and eighth embodiments, deformation can be prevented on the outer diameter side and inner diameter side of the annular plates 80a 3 and 80b 3 , that is, over the entire radial direction. The contact surfaces of the plates 80a 3 , 80b 3 can be prevented from unevenly contacting the opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the inboard side end portion 24b of the inner ring 20b or the caulking portion 13 of the hub ring 10, Early wear of the surface coating layers of the annular plates 80a 3 and 80b 3 can be suppressed, and the effect of suppressing stick-slip noise can be more reliably exhibited.

本発明は前述した実施形態に何ら限定されるものではなく、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内のすべての変更を含む。   The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

本発明における第一の実施形態で、環状プレートを内輪のインボード側端部と外側継手部材の肩部との間に介在させた駆動車輪用軸受装置を示す縦断面図である。1 is a longitudinal sectional view showing a drive wheel bearing device in which an annular plate is interposed between an inboard side end portion of an inner ring and a shoulder portion of an outer joint member in the first embodiment of the present invention. 本発明における第二の実施形態で、環状プレートをハブ輪の加締め部と外側継手部材の肩部との間に介在させた駆動車輪用軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the bearing apparatus for drive wheels which made the 2nd embodiment in this invention interpose the annular plate between the caulking part of the hub wheel and the shoulder part of the outer joint member. 本発明の第三の実施形態で、図１のタイプの駆動車輪用軸受装置に適用した例を示す要部拡大断面図である。It is principal part expanded sectional drawing which shows the example applied to the bearing apparatus for drive wheels of the type of FIG. 1 in 3rd embodiment of this invention. 本発明の第四の実施形態で、図２のタイプの駆動車輪用軸受装置に適用した例を示す要部拡大断面図である。FIG. 6 is an enlarged cross-sectional view of a main part showing an example applied to a drive wheel bearing device of the type of FIG. 2 in a fourth embodiment of the present invention. 本発明の第五の実施形態で、図１のタイプの駆動車輪用軸受装置に適用した例を示す要部拡大断面図である。It is principal part expanded sectional drawing which shows the example applied to the bearing apparatus for drive wheels of the type of FIG. 1 in 5th embodiment of this invention. 本発明の第六の実施形態で、図２のタイプの駆動車輪用軸受装置に適用した例を示す要部拡大断面図である。It is principal part expanded sectional drawing which shows the example applied to the bearing apparatus for drive wheels of the type of FIG. 2 in 6th embodiment of this invention. 本発明の第七の実施形態で、図１のタイプの駆動車輪用軸受装置に適用した例を示す要部拡大断面図である。It is principal part expanded sectional drawing which shows the example applied to the bearing apparatus for drive wheels of the type of FIG. 1 in 7th embodiment of this invention. 本発明の第八の実施形態で、図２のタイプの駆動車輪用軸受装置に適用した例を示す要部拡大断面図である。It is principal part expanded sectional drawing which shows the example applied to the bearing apparatus for drive wheels of the type of FIG. 2 in 8th embodiment of this invention. 駆動車輪用軸受装置の従来例を示す縦断面図である。It is a longitudinal cross-sectional view which shows the prior art example of the bearing apparatus for drive wheels.

符号の説明Explanation of symbols

１０ 内方部材（ハブ輪）
１２ 内側軌道面
１４ 車輪取付フランジ
２０ 内方部材（内輪）
２２ 内側軌道面
３０，４０ 転動体
５０ 外方部材（外輪）
５２，５４ 外側軌道面
６０ 等速自在継手
６１ 肩部
６２ 外側継手部材
６６ ステム部
８０ａ，８０ｂ 環状プレート 10 Inner member (hub ring)
12 Inner raceway surface 14 Wheel mounting flange 20 Inner member (inner ring)
22 Inner raceway surface 30, 40 Rolling element 50 Outer member (outer ring)
52, 54 Outer raceway surface 60 Constant velocity universal joint 61 Shoulder part 62 Outer joint member 66 Stem part 80a, 80b Annular plate

Claims (6)

内周に複列の外側軌道面が形成された外方部材と、一端に車輪取付フランジを有すると共に外周に複列の内側軌道面を有し、ハブ輪と内輪からなる内方部材と、前記外方部材の外側軌道面と内方部材の内側軌道面との間に介装された複列の転動体とを備え、前記ハブ輪の軸孔に等速自在継手の外側継手部材から延びるステム部を圧入してスプライン嵌合させた駆動車輪用軸受装置において、前記外側継手部材の肩部と前記内方部材の端部との対向面間に、表面コーティングにより所定の摺動特性を有する環状プレートを介在させ、前記環状プレートの接触面圧を３．０×１０6Ｐａ以下とし、前記環状プレートの外径を、外側継手部材の肩部と前記内方部材の端部の両対向面のうちでその外径が小さい方の部材の外径以下としたことを特徴とする駆動車輪用軸受装置。 An outer member having a double row outer raceway surface formed on the inner periphery, a wheel mounting flange at one end and a double row inner raceway surface on the outer periphery, and an inner member comprising a hub wheel and an inner ring; A double row rolling element interposed between the outer raceway surface of the outer member and the inner raceway surface of the inner member, and extending from the outer joint member of the constant velocity universal joint to the shaft hole of the hub wheel In a drive wheel bearing device in which a portion is press-fitted and fitted into a spline, an annular shape having a predetermined sliding characteristic by surface coating is provided between opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. A contact surface pressure of the annular plate is set to 3.0 × 10 6 Pa or less, and an outer diameter of the annular plate is set between a shoulder portion of the outer joint member and an end portion of the inner member. and characterized in that among the outer diameter is the outer diameter or less of a smaller member That the drive wheel bearing device. 内周に複列の外側軌道面が形成された外方部材と、一端に車輪取付フランジを有すると共に外周に複列の内側軌道面を有し、ハブ輪と内輪からなる内方部材と、前記外方部材の外側軌道面と内方部材の内側軌道面との間に介装された複列の転動体とを備え、前記ハブ輪の軸孔に等速自在継手の外側継手部材から延びるステム部を圧入してスプライン嵌合させた駆動車輪用軸受装置において、前記外側継手部材の肩部と前記内方部材の端部との対向面間に、表面コーティングにより所定の摺動特性を有する環状プレートを介在させ、前記環状プレートの接触面圧を３．０×１０6Ｐａ以下とし、前記環状プレートの内径を、外側継手部材の肩部と前記内方部材の端部の両対向面のうちでその内径が大きい方の部材の内径以上としたことを特徴とする駆動車輪用軸受装置。 An outer member having a double row outer raceway surface formed on the inner periphery, a wheel mounting flange at one end and a double row inner raceway surface on the outer periphery, and an inner member comprising a hub wheel and an inner ring; A double row rolling element interposed between the outer raceway surface of the outer member and the inner raceway surface of the inner member, and extending from the outer joint member of the constant velocity universal joint to the shaft hole of the hub wheel In a drive wheel bearing device in which a portion is press-fitted and fitted into a spline, an annular shape having a predetermined sliding characteristic by surface coating is provided between opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. A contact surface pressure of the annular plate is set to 3.0 × 10 6 Pa or less, and an inner diameter of the annular plate is set between the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. in a feature that it has equal to or greater than the inside diameter of the member towards its inside diameter is large That the drive wheel bearing device. 内周に複列の外側軌道面が形成された外方部材と、一端に車輪取付フランジを有すると共に外周に複列の内側軌道面を有し、ハブ輪と内輪からなる内方部材と、前記外方部材の外側軌道面と内方部材の内側軌道面との間に介装された複列の転動体とを備え、前記ハブ輪の軸孔に等速自在継手の外側継手部材から延びるステム部を圧入してスプライン嵌合させた駆動車輪用軸受装置において、前記外側継手部材の肩部と前記内方部材の端部との対向面間に、表面コーティングにより所定の摺動特性を有する環状プレートを介在させ、前記環状プレートの接触面圧を３．０×１０6Ｐａ以下とし、前記環状プレートの外径を、外側継手部材の肩部と前記内方部材の端部の両対向面のうちでその外径が小さい方の部材の外径以下とし、かつ、前記環状プレートの内径を、外側継手部材の肩部と前記内方部材の端部の両対向面のうちでその内径が大きい方の部材の内径以上としたことを特徴とする駆動車輪用軸受装置。 An outer member having a double row outer raceway surface formed on the inner periphery, a wheel mounting flange at one end and a double row inner raceway surface on the outer periphery, and an inner member comprising a hub wheel and an inner ring; A double row rolling element interposed between the outer raceway surface of the outer member and the inner raceway surface of the inner member, and extending from the outer joint member of the constant velocity universal joint to the shaft hole of the hub wheel In a drive wheel bearing device in which a portion is press-fitted and fitted into a spline, an annular shape having a predetermined sliding characteristic by surface coating is provided between opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner member. A contact surface pressure of the annular plate is set to 3.0 × 10 6 Pa or less, and an outer diameter of the annular plate is set between a shoulder portion of the outer joint member and an end portion of the inner member. The outer diameter of the member whose outer diameter is smaller than the outer diameter of the member, and the ring The inner diameter of the plate, the outer joint member of the shoulder portion and the inner member end driving wheel bearing apparatus characterized by an inner diameter and towards the member inner diameter than the larger among the two facing surfaces of the. 前記環状プレートが当接する外側継手部材の肩部あるいは内方部材の端部の少なくとも一方の対向面の平面度を０．１以下、かつ、直角度を０．１以下とした請求項１〜３のいずれか一項に記載の駆動車輪用軸受装置。 Said annular plate flatness of at least one of the opposing surfaces of the end portion of the shoulder or the inner member abutting against the outer joint member 0.1 or less, according to claim 1 to 3 in which the perpendicularity is 0.1 or less The bearing apparatus for drive wheels as described in any one of these . 前記ハブ輪の外周面に一対の内輪を嵌合させ、一方の内輪の外周面にアウトボード側の内側軌道面を形成し、他方の内輪の外周面にインボード側の内側軌道面を形成した請求項１〜４のいずれか一項に記載の駆動車輪用軸受装置。 A pair of inner rings are fitted to the outer peripheral surface of the hub wheel, an inner raceway surface on the outboard side is formed on the outer peripheral surface of one inner ring, and an inner raceway surface on the inboard side is formed on the outer peripheral surface of the other inner ring. The bearing apparatus for drive wheels as described in any one of Claims 1-4 . 前記一方の内側軌道面が形成されたハブ輪の外周面に小径段部を形成し、その小径段部に他方の内側軌道面が形成された内輪を圧入した上でハブ輪の小径段部の端部を加締めた請求項１〜４のいずれか一項に記載の駆動車輪用軸受装置。 A small-diameter step portion is formed on the outer peripheral surface of the hub wheel on which the one inner raceway surface is formed, and an inner ring on which the other inner raceway surface is formed is press-fitted into the small-diameter step portion. The bearing device for drive wheels as described in any one of Claims 1-4 which crimped the edge part.
JP2008161690A 2008-06-20 2008-06-20 Drive wheel bearing device Expired - Fee Related JP5207845B2 (en)

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