JP5594505B2 - Drive wheel bearing device - Google Patents

Drive wheel bearing device Download PDF

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JP5594505B2
JP5594505B2 JP2008078994A JP2008078994A JP5594505B2 JP 5594505 B2 JP5594505 B2 JP 5594505B2 JP 2008078994 A JP2008078994 A JP 2008078994A JP 2008078994 A JP2008078994 A JP 2008078994A JP 5594505 B2 JP5594505 B2 JP 5594505B2
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plate
coating layer
joint member
inner ring
outer joint
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JP2009234289A (en
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実 石島
拓志 手塚
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NTN Corp
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NTN Corp
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Priority to JP2008078994A priority Critical patent/JP5594505B2/en
Priority to PCT/JP2009/054637 priority patent/WO2009119313A1/en
Priority to US12/922,584 priority patent/US8591118B2/en
Priority to CN200980110558.2A priority patent/CN101980877B/en
Priority to EP09725468.4A priority patent/EP2263887B1/en
Publication of JP2009234289A publication Critical patent/JP2009234289A/en
Priority to US14/050,685 priority patent/US8783964B2/en
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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７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１２０、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. 7 illustrates a drive wheel bearing device. This bearing device includes a hub wheel 110 and an inner ring 120, 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、その外周面にアウトボード側の内側軌道面１１２が形成されると共に、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。このハブ輪１１０の外周面に形成された小径段部１１８に内輪１２０を嵌合させ、この内輪１２０の外周面にインボード側の内側軌道面１２２が形成されている。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。   The hub wheel 110 has an inner raceway surface 112 on the outboard side formed on the outer peripheral surface thereof, and includes a wheel mounting flange 114 for mounting a wheel (not shown). Hub bolts 116 for fixing the wheel disc are implanted at equal intervals in the circumferential direction of the wheel mounting flange 114. An inner ring 120 is fitted to a small-diameter step portion 118 formed on the outer peripheral surface of the hub wheel 110, and an inner raceway surface 122 on the inboard side is formed on the outer peripheral surface of the inner ring 120. 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.

内輪１２０は、クリープを防ぐために適当な締め代をもってハブ輪１１０の小径段部１１８に圧入されている。ハブ輪１１０の外周面に形成されたアウトボード側の内側軌道面１１２と、内輪１２０の外周面に形成されたインボード側の内側軌道面１２２とで複列の内側軌道面を構成している。この内輪１２０をハブ輪１１０の小径段部１１８に圧入し、ハブ輪１１０の小径段部１１８の端部を外側に加締めることにより、その加締め部１１３でもって内輪１２０を抜け止めしてハブ輪１１０と一体化し、軸受部１７０に予圧を付与している。   The inner ring 120 is press-fitted into the small-diameter step portion 118 of the hub ring 110 with an appropriate tightening margin to prevent creep. An outboard-side inner raceway surface 112 formed on the outer peripheral surface of the hub wheel 110 and an inboard-side inner raceway surface 122 formed on the outer peripheral surface of the inner ring 120 constitute a double-row inner raceway surface. . The inner ring 120 is press-fitted into the small-diameter step portion 118 of the hub wheel 110, and the end portion of the small-diameter step portion 118 of the hub wheel 110 is crimped to the outside, so that the inner ring 120 is prevented from being detached by the crimping portion 113. The bearing 110 is integrated with the ring 110 to apply a preload.

外輪１５０は、内周面にハブ輪１１０および内輪１２０の内側軌道面１１２，１２２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 is formed with double row outer race surfaces 152, 154 facing the inner race surfaces 112, 122 of the hub wheel 110 and the inner ring 120 on the inner circumferential surface, and a vehicle body mounting flange for mounting to the vehicle body (not shown). 156. 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、ハブ輪１１０および内輪１２０の外周面に形成された内側軌道面１１２，１２２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 has inner raceway surfaces 112 and 122 formed on the outer peripheral surfaces of the hub wheel 110 and the inner ring 120 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 held by the cages 132 and 142 so as to be rotatable at equal intervals in the circumferential direction.

軸受部１７０の両端開口部には、ハブ輪１１０と内輪１２０の外周面に摺接するように、外輪１５０とハブ輪１１０および内輪１２０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 that seal the annular space between the outer ring 150, the hub ring 110, and the inner ring 120 so as to be in sliding contact with the outer peripheral surfaces of the hub ring 110 and the inner ring 120 are formed at both ends of the bearing portion 170. Are fitted to the inner diameters of both ends of the inner wall, and prevent leakage of 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、ハブ輪１１０の加締め部１１３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。   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, by tightening the nut 172 to the male screw portion 165 formed at the end portion of the stem portion 166 in a state where the facing surface of the caulking portion 113 of the hub wheel 110 and the shoulder portion 161 of the outer joint member 162 face each other. The constant velocity universal joint 160 is fixed to the hub wheel 110.

ところで、前述した駆動輪用軸受装置では、軸受部１７０のハブ輪１１０の加締め部１１３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のハブ輪１１０の加締め部１１３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。   By the way, in the drive wheel bearing device described above, the caulking portion 113 of the hub wheel 110 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 occur between the caulking portion 113 of the hub wheel 110 of the 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のハブ輪１１０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、ハブ輪１１０の加締め部１１３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 generated via the male and female splines 111 and 168 when rotational torque is applied from the outer joint member 162 of the constant velocity universal joint 160 to the hub wheel 110 of the bearing portion 170 that is stationary when the vehicle starts. In this case, rotational torque is transmitted from the outer joint member 162 to the hub wheel 110. However, due to the transmission torque fluctuation between the outer joint member 162 and the bearing portion 170 and torsion of the outer joint member 162, the caulking portion of the hub wheel 110 is A sudden slip occurs between 113 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のインボード側端部と外側継手部材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 stick-slip noise described above, a means (for example, a plate having excellent sliding characteristics) is sandwiched between the opposing surfaces of the inboard side end portion of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162 (for example, Patent Documents 1 and 2).

これら特許文献１，２では、軸受部１７０のインボード側端部と外側継手部材１６２の肩部１６１との対向面間にプレートを介在させることにより、その軸受部１７０のインボード側端部と外側継手部材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, by interposing a plate between the opposing surfaces of the inboard side end portion of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162, the inboard side end portion of the bearing portion 170 The frictional resistance between the outer joint member 162 and the shoulder portion 161 is reduced so as to cause positive slip, so that a stick slip noise is not generated without causing a sudden slip.
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のインボード側端部と外側継手部材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。   Incidentally, in the bearing devices disclosed in Patent Documents 1 and 2, as described above, the sliding characteristics are excellent between the facing surfaces of the inboard side end portion of the bearing portion 170 and the shoulder portion 161 of the outer joint member 162. In addition, the occurrence of stick-slip noise is prevented by interposing an annular plate.

しかしながら、これら軸受装置で、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る軸力でもって等速自在継手１６０をハブ輪１１０に固定しているが、その軸力によりプレートに加わる大きな面圧でもってそのプレートが変形したりすることによって、軸力が低下してしまう可能性がある。このような軸力の低下が生じると、軸受部１７０の耐久性が損なわれるという不具合が発生する。また、プレート自体の防錆性能が低い場合、錆によりプレートの耐スティックスリップ性が損なわれ、錆によりプレートの厚みが小さくなり、軸力の低下を招くおそれがある。   However, in these bearing devices, the constant velocity universal joint 160 is fixed to the hub wheel 110 with an axial force by tightening the nut 172 to the male screw portion 165 formed at the end portion of the stem portion 166. If the plate is deformed by a large surface pressure applied to the plate, the axial force may be reduced. When such a reduction in the axial force occurs, a problem that the durability of the bearing portion 170 is impaired occurs. Moreover, when the rust prevention performance of the plate itself is low, the stick-slip resistance of the plate is impaired by the rust, and the thickness of the plate is reduced by the rust, which may cause a reduction in the axial force.

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、軸力の低下を長期に亘って防止し、耐スティックスリップ性を確保し得る駆動車輪用軸受装置を提供することにある。   Accordingly, the present invention has been proposed in view of the above-described problems, and the object of the present invention is to provide a bearing device for a drive wheel that can prevent a reduction in axial force over a long period of time and ensure stick-slip resistance. Is to provide.

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スプライン嵌合させ、内輪の端部を外側継手部材の肩部と対向させ、ステム部の端部に形成された雄ねじ部にナットを締め付けることによって等速自在継手をハブ輪に固定し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輪の端部との対向面間に、摺動特性の優れたコーティング層が形成され、かつ、板厚が０．５ｍｍ〜２ｍｍを有するステンレス鋼製のプレートを介在させ、軸力により面圧が加わるプレートの耐力を２０５Ｎ／ｍｍ2以上とし、プレートは、外側継手部材の肩部と内輪の端部との二つの対向面間に介在する環状部と、その環状部の周縁を軸方向に延在して内輪の端部に嵌合させた筒状部とで構成され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. The stem portion extending from the outer joint member of the constant velocity universal joint is spline-fitted into the shaft hole of the constant velocity joint, the end of the inner ring is opposed to the shoulder portion of the outer joint member, and the nut is formed on the male thread formed at the end of the stem portion. In the drive wheel bearing device in which the constant velocity universal joint is fixed to the hub wheel by tightening the bolt, a coating layer having excellent sliding characteristics is formed between the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner ring. Made of stainless steel having a thickness of 0.5 mm to 2 mm Plates are interposed, the yield strength of the plate in the surface pressure exerted by the axial forces and 205N / mm 2 or more, the plate includes an annular portion interposed between the two opposing surfaces of the shoulder portion of the outer joint member and the inner ring of the end The annular portion extends in the axial direction and is formed by a cylindrical portion fitted to the end of the inner ring .

本発明では、外側継手部材の肩部と内輪の端部との対向面間に、モリブデンコーティング層またはフッ素樹脂コーティング層の形成により摺動特性の優れた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, an inner member is formed by interposing a plate having excellent sliding characteristics by forming a molybdenum coating layer or a fluororesin coating layer between opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner ring. Even if the transmission torque fluctuation between the bearing part having the bearing and the outer joint member and the torsion of the outer joint member occur, the frictional resistance between the bearing part and the outer joint member is reduced, and positive slip occurs. By doing so, 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.

また、摺動特性の優れたプレートの厚みを０．５ｍｍ以上とすることで、プレートの強度を確保し、軸力によりプレートに加わる大きな面圧でもってそのプレートが変形したりすることを防止して軸力の低下を未然に防止する。一方、プレートの厚みを２ｍｍ以下とすることで、軸受装置の軸方向寸法を大きくすることなく、コンパクトな設計を確保することができる。   In addition, by setting the thickness of the plate with excellent sliding characteristics to 0.5 mm or more, the strength of the plate is secured and the plate is prevented from being deformed by a large surface pressure applied to the plate by the axial force. This prevents a decrease in axial force. On the other hand, by setting the plate thickness to 2 mm or less, a compact design can be ensured without increasing the axial dimension of the bearing device.

本発明におけるモリブデンコーティング層またはフッ素樹脂コーティング層の膜厚は２μｍ〜３０μｍとすることが望ましい。モリブデンコーティング層またはフッ素樹脂コーティング層の膜厚を２μｍ以上とすれば、モリブデンコーティング層またはフッ素樹脂コーティング層が早期に摩滅することはない。また、モリブデンコーティング層またはフッ素樹脂コーティング層の膜厚を３０μｍ以下とすれば、コーティング材の使用量を必要最小限に抑えることでコストアップを招くこともなく、軸力によりプレートに大きな面圧が加わっても、コーティング層の潰れを小さく出来るので、軸力の低下を防止できて軸受部の耐久性を確保できる。   The film thickness of the molybdenum coating layer or the fluororesin coating layer in the present invention is desirably 2 μm to 30 μm. If the film thickness of the molybdenum coating layer or the fluororesin coating layer is 2 μm or more, the molybdenum coating layer or the fluororesin coating layer will not be worn out at an early stage. In addition, if the film thickness of the molybdenum coating layer or the fluororesin coating layer is 30 μm or less, there is no cost increase by minimizing the amount of coating material used, and a large surface pressure is applied to the plate by the axial force. Even if added, since the collapse of the coating layer can be reduced, the reduction of the axial force can be prevented and the durability of the bearing portion can be ensured.

本発明におけるプレートの材質はステンレス鋼とする。これにより、プレート自体に防錆作用を発揮させることができ、錆の発生を未然に防止でき、自動車などの長期に亘る防錆性能を要求される使用環境にも対応可能となる。 The material of the plates in the present invention shall be the stainless steel. As a result , the rust preventive action can be exerted on the plate itself, the occurrence of rust can be prevented in advance, and it is possible to cope with the use environment that requires long-term rust prevention performance such as automobiles.

本発明におけるプレートの耐力は２０５Ｎ／ｍｍ2以上とする。これにより、軸力によりプレートに大きな面圧が加わっても、プレートの変形を防止することができ、軸力の低下を未然に防止できる。 Strength of the plate in the present invention shall be the 205N / mm 2 or more. Thereby , even if a large surface pressure is applied to the plate by the axial force, the deformation of the plate can be prevented, and the reduction of the axial force can be prevented beforehand.

また、本発明におけるプレートは、外側継手部材の肩部と内輪の端部との二つの対向面間に介在する環状部と、その環状部の周縁を軸方向に延在して内輪の端部に嵌合させた筒状部とからなる構造を具備する。このような構造を具備することにより、プレートの筒状部を内輪の端部に嵌合することで、プレートを内輪に組み付けた状態で環状部を内輪の端部と外側継手部材の肩部との二つの対向面間に容易に位置決めした状態で介在させることができる。 Further, the plate according to the present invention includes an annular portion interposed between two opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner ring, and an end portion of the inner ring extending in the axial direction at the periphery of the annular portion. The structure which consists of a cylindrical part fitted to is comprised . By having such a structure , by fitting the cylindrical portion of the plate to the end portion of the inner ring, the annular portion is connected to the end portion of the inner ring and the shoulder portion of the outer joint member in a state where the plate is assembled to the inner ring. Between the two opposing surfaces can be easily positioned.

本発明では、外側継手部材の肩部と内輪の端部との対向面間に、モリブデンコーティング層またはフッ素樹脂コーティング層の形成により摺動特性の優れた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 the present invention, a plate having excellent sliding characteristics is formed by forming a molybdenum coating layer or a fluororesin coating layer between opposed surfaces of the shoulder portion of the outer joint member and the end portion of the inner ring . 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.

また、摺動特性の優れたステンレス鋼製のプレートの厚みを０．５ｍｍ〜２ｍｍとし、そのプレートの耐力を２０５Ｎ／ｍｍ 2 以上とすることで、プレートの強度を確保し、軸力によりプレートに加わる大きな面圧でもってそのプレートが変形したりすることを防止して軸力の低下を長期に亘って防止し、耐スティックスリップ性を確保すると共に、コンパクトな駆動車輪用軸受装置を提供することができる。 In addition, the thickness of the stainless steel plate with excellent sliding characteristics is set to 0.5 mm to 2 mm, and the proof stress of the plate is set to 205 N / mm 2 or more, so that the strength of the plate is secured and the plate is driven by the axial force. The plate is prevented from being deformed by a large surface pressure applied to the shaft to prevent the axial force from deteriorating over a long period of time, ensuring stick-slip resistance and providing a compact drive wheel bearing device. be able to.

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２０、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（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 is mainly composed of the hub ring 10 and the inner ring 20, which are inner members, double row rolling elements 30, 40, the outer ring 50 which is an outer member, and a constant velocity universal joint 60. As a component. In the following description, the side closer to the outside of the vehicle in a state assembled to the vehicle is referred to as an outboard (left side in the drawing), and the side closer to the center is referred to as an inboard side (right side in the drawing).

ハブ輪１０は、その外周面にアウトボード側の内側軌道面１２が形成されると共に、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。このハブ輪１０の外周面に形成された小径段部１８に内輪２０を嵌合させ、この内輪２０の外周面にインボード側の内側軌道面２２が形成されている。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。   The hub wheel 10 has an inner raceway surface 12 on the outboard side formed on the outer peripheral surface thereof, and includes a wheel mounting flange 14 for mounting a wheel (not shown). Hub bolts 16 for fixing the wheel disc are implanted at equal intervals in the circumferential direction of the wheel mounting flange 14. An inner ring 20 is fitted to a small diameter step portion 18 formed on the outer peripheral surface of the hub wheel 10, and an inner raceway surface 22 on the inboard side is formed on the outer peripheral surface of the inner ring 20. 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.

内輪２０は、クリープを防ぐために適当な締め代をもってハブ輪１０の小径段部１８に圧入されている。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。   The inner ring 20 is press-fitted into the small-diameter step portion 18 of the hub ring 10 with an appropriate tightening margin to prevent creep. 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 constitute a double row inner 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.

外輪５０は、内周面にハブ輪１０および内輪２０の内側軌道面１２，２２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 12 and 22 of the hub wheel 10 and the inner ring 20 on the inner circumferential surface, and a vehicle body mounting flange for mounting to the vehicle body (not shown). 56. 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、ハブ輪１０および内輪２０の外周面に形成された内側軌道面１２，２２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 has inner raceway surfaces 12 and 22 formed on the outer peripheral surfaces of the hub wheel 10 and the inner ring 20 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 between the rolling elements 30 and 40, and the rolling elements 30 and 40 in each row are rotatably held by the cages 32 and 42 at equal intervals in the circumferential direction.

軸受部７０の両端開口部には、ハブ輪１０と内輪２０の外周面に摺接するように、外輪５０とハブ輪１０および内輪２０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 and 44 that seal the annular space between the outer ring 50, the hub ring 10, and the inner ring 20 are provided at both ends of the bearing portion 70 so as to be in sliding contact with the outer peripheral surfaces of the hub ring 10 and the inner ring 20. Are fitted to the inner diameters of both end portions of the nozzle, and prevent leakage of grease filled therein 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とハブ輪１０の加締め部１３との対向面間に摺動特性の優れた環状のプレート８０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。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 80 having excellent sliding characteristics is interposed between the opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the crimped portion 13 of the hub wheel 10, and the stem portion 66. 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. 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とハブ輪１０の加締め部１３との対向面間にプレート８０を挟み込んだ構造としている。外側継手部材６２の肩部６１とハブ輪１０の加締め部１３との対向面間に介在されたプレート８０は、モリブデン（ＭｏＳ２）コーティング層またはフッ素樹脂コーティング層８１が形成され、かつ、板厚が０．５ｍｍ〜２ｍｍを有する。なお、このプレート８０の厚みとしては、０．８ｍｍ〜１ｍｍが好ましい。 The plate 80 is sandwiched 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 with a predetermined tightening force (axial force) by the nut 72. The plate 80 interposed 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 has a molybdenum (MoS 2 ) coating layer or a fluororesin coating layer 81 formed thereon, and a plate The thickness is 0.5 mm to 2 mm. In addition, as thickness of this plate 80, 0.8 mm-1 mm are preferable.

このように、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、モリブデンコーティング層またはフッ素樹脂コーティング層８１の形成により摺動特性の優れたプレート８０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。   In this way, the plate 80 having excellent sliding characteristics is formed by forming the molybdenum coating layer or the fluororesin coating layer 81 between the facing surfaces of the shoulder portion 61 of the outer joint member 62 and the crimped portion 13 of the hub wheel 10. As a result, even if the transmission torque fluctuation between the bearing portion 70 and the outer joint member 62 and the torsion of the outer joint member 62 occur, the frictional resistance between the bearing portion 70 and the outer joint member 62 is reduced. Thus, by making positive slip occur, it is possible to prevent the occurrence of stick-slip noise without causing a sudden slip between the bearing portion 70 and the outer joint member 62.

また、摺動特性の優れたプレート８０の厚みを０．５ｍｍ以上とすることで、プレート８０の強度を確保し、軸力によりプレート８０に加わる大きな面圧でもってそのプレート８０が変形したりすることを防止して軸力の低下を長期に亘って防止し、耐スティックスリップ性を確保する。一方、プレート８０の厚みを２ｍｍ以下とすることで、軸受装置の軸方向寸法を大きくすることなく、コンパクトな設計を確保することができる。   Further, by setting the thickness of the plate 80 having excellent sliding characteristics to 0.5 mm or more, the strength of the plate 80 is secured, and the plate 80 is deformed by a large surface pressure applied to the plate 80 by an axial force. This prevents the reduction of the axial force over a long period of time and secures the stick-slip resistance. On the other hand, when the thickness of the plate 80 is 2 mm or less, a compact design can be ensured without increasing the axial dimension of the bearing device.

このプレート８０の厚みが０．５ｍｍよりも小さいと、プレート８０の強度を確保することが困難となり、軸力により大きな面圧が加わった場合に変形し易く、軸力の低下を招くおそれがあり、プレート８０の破損を引き起こす原因となる。また、プレート８０の厚みが２ｍｍよりも大きくなると、軸受装置の軸方向寸法が大きくなって装置のコンパクト化が困難となる。   If the thickness of the plate 80 is smaller than 0.5 mm, it is difficult to ensure the strength of the plate 80, and it is likely to be deformed when a large surface pressure is applied by the axial force, which may cause a reduction in the axial force. This causes damage to the plate 80. Further, when the thickness of the plate 80 is larger than 2 mm, the axial dimension of the bearing device becomes large, and it becomes difficult to make the device compact.

プレート８０に形成されたモリブデンコーティング層またはフッ素樹脂コーティング層８１の膜厚は２μｍ〜３０μｍとしている。モリブデンコーティング層またはフッ素樹脂コーティング層８１の膜厚を２μｍ以上とすれば、モリブデンコーティング層またはフッ素樹脂コーティング層８１が早期に摩滅することはない。また、モリブデンコーティング層またはフッ素樹脂コーティング層８１の膜厚を３０μｍ以下とすれば、コーティング材の使用量を必要最小限に抑えることでコストアップを招くこともなく、軸力によりプレート８０に大きな面圧が加わっても、コーティング層８１自体が潰れることがないので、軸力の低下を防止できてナット７２のゆるみを防止できる。   The film thickness of the molybdenum coating layer or the fluororesin coating layer 81 formed on the plate 80 is 2 μm to 30 μm. If the film thickness of the molybdenum coating layer or the fluororesin coating layer 81 is 2 μm or more, the molybdenum coating layer or the fluororesin coating layer 81 will not be worn out at an early stage. Further, if the film thickness of the molybdenum coating layer or the fluororesin coating layer 81 is 30 μm or less, the use amount of the coating material is kept to a minimum and the cost is not increased. Even if pressure is applied, the coating layer 81 itself is not crushed, so that a reduction in axial force can be prevented, and loosening of the nut 72 can be prevented.

このコーティング層８１の膜厚が２μｍよりも小さいと、コーティング層８１が早期に摩滅する可能性がある。また、コーティング層８１の膜厚が３０μｍよりも大きいと、コーティング材の使用量が増加してコストアップを招くことになり、軸力によりプレート８０に大きな面圧が加わった場合にコーティング層８１自体が潰れることで軸力の低下を招き、軸受部７０の耐久性が損なわれる可能性がある。   If the thickness of the coating layer 81 is smaller than 2 μm, the coating layer 81 may be worn away at an early stage. If the coating layer 81 has a thickness greater than 30 μm, the amount of coating material used increases, leading to an increase in cost. When a large surface pressure is applied to the plate 80 by an axial force, the coating layer 81 itself is used. As a result, the axial force is reduced, and the durability of the bearing portion 70 may be impaired.

プレート８０の材質はステンレス鋼としている。このように、プレート８０をステンレス鋼で構成することにより、プレート８０自体に防錆作用を発揮させることができ、錆の発生を未然に防止でき、自動車などの長期に亘る防錆性能を要求される使用環境にも対応可能となる。   The material of the plate 80 is stainless steel. As described above, the plate 80 is made of stainless steel, so that the plate 80 itself can exert a rust preventive action, can prevent the occurrence of rust, and is required to have a long-term rust preventive performance such as an automobile. It is possible to correspond to the usage environment.

また、プレート８０の耐力を２０５Ｎ／ｍｍ２以上としている。このように、プレート８０の耐力を２０５Ｎ／ｍｍ２以上とすることにより、軸力によりプレート８０に大きな面圧が加わっても、プレート８０の変形を防止することができ、軸力の低下を未然に防止できる。 Further, the proof stress of the plate 80 is set to 205 N / mm 2 or more. Thus, by setting the proof stress of the plate 80 to 205 N / mm 2 or more, even if a large surface pressure is applied to the plate 80 by the axial force, the deformation of the plate 80 can be prevented, and the axial force is reduced. Can be prevented.

以上で説明した第一の実施形態では、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 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. Although the case where the inner ring 20 is press-fitted and applied to a bearing device in which the end of the small-diameter stepped portion 18 of the hub wheel 10 is crimped has been described, the present invention is not limited to this.

例えば、図２に示すように、ハブ輪１０の外周面に一対の内輪２０ａ，２０ｂを嵌合させ、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を形成し、他方の内輪２０ｂの外周面にインボード側の内側軌道面２２ｂを形成し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 pair of inner rings 20a and 20b are fitted to the outer peripheral surface of the hub wheel 10, an inner raceway surface 22a on the outboard side is formed on the outer peripheral surface of one inner ring 20a, and the other inner ring The present invention is also applicable to a type of bearing device in which an inner raceway surface 22b on the inboard side is formed on the outer peripheral surface of 20b.

図２に示す第二の実施形態では、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を外側継手部材６２の肩部６１と対向させた構造となる。従って、第一の実施形態で説明したプレート８０は、内輪２０ｂのインボード側端部と外側継手部材６２の肩部６１との間に介在させることになる。なお、このプレート８０の構成、つまり、モリブデンコーティング層またはフッ素樹脂コーティング層８１が形成され、かつ、板厚が０．５ｍｍ〜２ｍｍを有する点、モリブデンコーティング層またはフッ素樹脂コーティング層８１の膜厚を２μｍ〜３０μｍとする点、材質をステンレス鋼とする点、耐力を２０５Ｎ／ｍｍ２以上とする点、およびその作用効果については、前述した第一の実施形態と同様であるため、重複説明は省略するが、第二の実施形態においては、軸力の低下による軸受部７０の耐久性低下を防止する効果もある。 In the second embodiment shown in FIG. 2, the inboard side end of the other inner ring 20 b located on the inboard side is opposed to the shoulder 61 of the outer joint member 62. Therefore, the plate 80 described in the first embodiment is interposed between the inboard side end portion of the inner ring 20 b and the shoulder portion 61 of the outer joint member 62. The configuration of the plate 80, that is, the point where the molybdenum coating layer or the fluororesin coating layer 81 is formed and the plate thickness is 0.5 mm to 2 mm, and the film thickness of the molybdenum coating layer or the fluororesin coating layer 81 is as follows. The point of 2 μm to 30 μm, the point of material of stainless steel, the point of proof stress of 205 N / mm 2 or more, and the function and effect thereof are the same as in the first embodiment described above, and therefore redundant description is omitted. However, in the second embodiment, there is an effect of preventing a decrease in durability of the bearing portion 70 due to a decrease in axial force.

また、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では、環状のプレート８０を使用した場合について説明したが、図３に示す第三の実施形態および図４に示す第四の実施形態のように、環状部８２ａおよび筒状部８２ｂを有するプレート８２を使用することも可能である。図３に示す第三の実施形態は、第一の実施形態と同様、ハブ輪１０の小径段部１８の端部を加締めたタイプの軸受装置に適用したもので、図４に示す第四の実施形態は、第二の実施形態と同様、ハブ輪１０の外周面に一対の内輪２０ａ，２０ｂを嵌合させたタイプの軸受装置に適用したものである。   Further, in the first embodiment shown in FIG. 1 and the second embodiment shown in FIG. 2, the case where the annular plate 80 is used has been described, but the third embodiment shown in FIG. 3 and FIG. 4 show. As in the fourth embodiment, a plate 82 having an annular portion 82a and a cylindrical portion 82b can be used. As in the first embodiment, the third embodiment shown in FIG. 3 is applied to a bearing device in which the end of the small-diameter step portion 18 of the hub wheel 10 is crimped. The fourth embodiment shown in FIG. This embodiment is applied to a bearing device of a type in which a pair of inner rings 20a and 20b are fitted to the outer peripheral surface of the hub wheel 10 as in the second embodiment.

第三の実施形態におけるプレート８２は、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３との二つの対向面間に介在する環状部８２ａと、その環状部８２ａの外周縁を軸方向インボード側へ延在して外側継手部材６２の肩部６１に嵌合させた筒状部８２ｂとからなる構造を有する。同様に、第四の実施形態におけるプレート８２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との二つの対向面間に介在する環状部８２ａと、その環状部８２ａの外周縁を軸方向インボード側へ延在して外側継手部材６２の肩部６１に嵌合させた筒状部８２ｂとからなる構造を有する。   The plate 82 in the third embodiment has an annular portion 82a interposed between two opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the crimped portion 13 of the hub wheel 10, and an outer peripheral edge of the annular portion 82a. It has a structure including a cylindrical portion 82 b extending to the inboard side in the axial direction and fitted to the shoulder portion 61 of the outer joint member 62. Similarly, the plate 82 in the fourth embodiment includes an annular portion 82a interposed between two opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the inboard side end portion of the inner ring 20b, and the annular portion 82a. The outer peripheral edge extends to the inboard side in the axial direction, and has a structure including a cylindrical portion 82 b fitted to the shoulder portion 61 of the outer joint member 62.

これらプレート８２は、モリブデンコーティング層またはフッ素樹脂コーティング層８３が形成され、かつ、板厚が０．５ｍｍ〜２ｍｍを有する。また、プレート８２に形成されたモリブデンコーティング層またはフッ素樹脂コーティング層８３の膜厚は２μｍ〜３０μｍとしている。さらに、プレート８２の材質はステンレス鋼とし、その耐力を２０５Ｎ／ｍｍ２以上としている。以上の構成としたことによるプレート８２の環状部８２ａが発揮する作用効果については、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における環状のプレート８０と同様であるため、重複説明は省略する。 These plates 82 have a molybdenum coating layer or a fluororesin coating layer 83 formed thereon, and have a plate thickness of 0.5 mm to 2 mm. The film thickness of the molybdenum coating layer or the fluororesin coating layer 83 formed on the plate 82 is 2 μm to 30 μm. Furthermore, the material of the plate 82 is stainless steel, and the proof stress is 205 N / mm 2 or more. The operational effects exerted by the annular portion 82a of the plate 82 by the above configuration are the same as those of the annular plate 80 in the first embodiment shown in FIG. 1 and the second embodiment shown in FIG. Duplicate explanation is omitted.

このような構造のプレート８２を使用することにより、プレート８２の筒状部８２ｂを外側継手部材６２の肩部６１に嵌合することで、プレート８２を外側継手部材６２に組み付けることができ、プレート８２の取り扱いが容易となる。また、プレート８２の環状部８２ａを、第三の実施形態の場合、ハブ輪１０の加締め部１３と外側継手部材６２の肩部６１との対向面間に容易に位置決めすることができ、第四の実施形態の場合、内輪２０ｂのインボード側端部と外側継手部材６２の肩部６１との対向面間に容易に位置決めすることができる。   By using the plate 82 having such a structure, the plate 82 can be assembled to the outer joint member 62 by fitting the cylindrical portion 82b of the plate 82 to the shoulder portion 61 of the outer joint member 62. The handling of 82 becomes easy. Further, in the case of the third embodiment, the annular portion 82a of the plate 82 can be easily positioned between the facing surfaces of the caulking portion 13 of the hub wheel 10 and the shoulder portion 61 of the outer joint member 62. In the case of the fourth embodiment, the positioning can be easily performed between the opposing surfaces of the inboard side end portion of the inner ring 20 b and the shoulder portion 61 of the outer joint member 62.

図３に示す第三の実施形態および図４に示す第四の実施形態では、プレート８２が、環状部８２ａの外周縁を軸方向インボード側へ延在して筒状部８２ｂを外側継手部材６２の肩部６１に嵌合させた構造を有し、プレート８２を外側継手部材６２に組み付けることを可能に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なく、図５に示す第五の実施形態および図６に示す第六の実施形態のような構造を具備したプレート８４，８６を使用することも可能である。   In the third embodiment shown in FIG. 3 and the fourth embodiment shown in FIG. 4, the plate 82 extends the outer peripheral edge of the annular portion 82 a toward the axial inboard side, and the cylindrical portion 82 b becomes the outer joint member. 62, the case where the plate 82 can be assembled to the outer joint member 62 has been described. However, the present invention is not limited to this and is shown in FIG. It is also possible to use the plates 84 and 86 having the structure as in the fifth embodiment and the sixth embodiment shown in FIG.

なお、図５に示す第五の実施形態は、第三の実施形態と同様、ハブ輪１０の小径段部１８の端部を加締めたタイプの軸受装置に適用したもので、図６に示す第六の実施形態は、第四の実施形態と同様、ハブ輪１０の外周面に一対の内輪２０ａ，２０ｂを嵌合させたタイプの軸受装置に適用したものである。   The fifth embodiment shown in FIG. 5 is applied to a bearing device in which the end of the small-diameter step portion 18 of the hub wheel 10 is caulked, as in the third embodiment, and is shown in FIG. As in the fourth embodiment, the sixth embodiment is applied to a type of bearing device in which a pair of inner rings 20a and 20b are fitted to the outer peripheral surface of the hub wheel 10.

第五の実施形態におけるプレート８４は、外側継手部材６２の肩部６１とハブ輪１０の加締め部１３との二つの対向面間に介在する環状部８４ａと、その環状部８４ａの外周縁を軸方向アウトボード側へ延在して内輪２０のインボード側端部に嵌合させた筒状部８４ｂとからなる構造を有する。一方、第六の実施形態におけるプレート８６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との二つの対向面間に介在する環状部８４ａと、その環状部８４ａの内周縁を軸方向アウトボード側へ延在して内輪２０ｂのインボード側端部に嵌合された筒状部８６ｂとからなる構造を有する。   The plate 84 in the fifth embodiment includes an annular portion 84a interposed between two opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the crimped portion 13 of the hub wheel 10, and an outer peripheral edge of the annular portion 84a. It has a structure comprising a cylindrical portion 84b extending to the axial outboard side and fitted to the inboard side end portion of the inner ring 20. On the other hand, the plate 86 in the sixth embodiment includes an annular portion 84a interposed between two opposing surfaces of the shoulder portion 61 of the outer joint member 62 and the inboard side end portion of the inner ring 20b, and an inner portion of the annular portion 84a. It has a structure comprising a cylindrical portion 86b that extends to the outboard side in the axial direction and is fitted to the end portion on the inboard side of the inner ring 20b.

これらプレート８４，８６は、モリブデンコーティング層またはフッ素樹脂コーティング層８５，８７が形成され、かつ、板厚が０．５ｍｍ〜２ｍｍを有する。また、プレート８４，８６に形成されたモリブデンコーティング層またはフッ素樹脂コーティング層８５，８７の膜厚は２μｍ〜３０μｍとしている。さらに、プレート８４，８６の材質はステンレス鋼とし、その耐力を２０５Ｎ／ｍｍ２以上としている。以上の構成としたことによるプレート８４，８６の環状部８４ａ，８６ａが発揮する作用効果については、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における環状のプレート８０と同様であるため、重複説明は省略する。 These plates 84 and 86 have molybdenum coating layers or fluororesin coating layers 85 and 87 formed thereon, and have a plate thickness of 0.5 mm to 2 mm. The film thickness of the molybdenum coating layer or the fluororesin coating layers 85 and 87 formed on the plates 84 and 86 is 2 μm to 30 μm. Furthermore, the material of the plates 84 and 86 is stainless steel, and the proof stress is 205 N / mm 2 or more. About the effect which the annular parts 84a and 86a of the plates 84 and 86 exhibit by having set it as the above structure, with the cyclic | annular plate 80 in 1st embodiment shown in FIG. 1, and 2nd embodiment shown in FIG. Since it is the same, redundant description is omitted.

このような構造のプレート８４，８６を使用することにより、第五の実施形態の場合、プレート８４の筒状部８４ｂをハブ輪１０の加締め部１３に嵌合し、第六の実施形態の場合、プレート８６の筒状部８６ｂを内輪２０ｂのインボード側端部に嵌合することで、これらプレート８４，８６を軸受部７０に組み付けることができ、プレート８４，８６の取り扱いが容易となる。また、第五の実施形態の場合、プレート８４の環状部８４ａをハブ輪１０の加締め部１３と外側継手部材６２の肩部６１との対向面間に容易に位置決めすることができ、第六の実施形態の場合、プレート８６の環状部８６ｂを内輪２０ｂのインボード側端部と外側継手部材６２の肩部６１との対向面間に容易に位置決めすることができる。   By using the plates 84 and 86 having such a structure, in the case of the fifth embodiment, the cylindrical portion 84b of the plate 84 is fitted to the caulking portion 13 of the hub wheel 10, and the sixth embodiment is used. In this case, by fitting the cylindrical portion 86b of the plate 86 to the inboard side end portion of the inner ring 20b, the plates 84 and 86 can be assembled to the bearing portion 70, and the handling of the plates 84 and 86 becomes easy. . Further, in the case of the fifth embodiment, the annular portion 84a of the plate 84 can be easily positioned between the facing surfaces of the caulking portion 13 of the hub wheel 10 and the shoulder portion 61 of the outer joint member 62. In the case of this embodiment, the annular portion 86b of the plate 86 can be easily positioned between the opposing surfaces of the inboard side end portion of the inner ring 20b and the shoulder portion 61 of the outer joint member 62.

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、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適用例を示す縦断面図である。FIG. 5 is a longitudinal sectional view showing an application example in which the plate is interposed between the caulking portion of the hub wheel and the shoulder portion of the 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、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適用例を示す縦断面図である。In 2nd embodiment in this invention, it is a longitudinal cross-sectional view which shows the application example which interposed the plate between the inboard side edge part of the inner ring | wheel, and the shoulder part of an outer joint member. 本発明における第三の実施形態で、外側継手部材に組み付けられた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適用例を示す縦断面図である。In the third embodiment of the present invention, it is a longitudinal sectional view showing an application example in which the plate assembled to the outer joint member is interposed between the caulking portion of the hub wheel and the shoulder portion of the outer joint member. 本発明における第四の実施形態で、外側継手部材に組み付けられた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適用例を示す縦断面図である。In 4th embodiment in this invention, it is a longitudinal cross-sectional view which shows the application example which interposed the plate assembled | attached to the outer joint member between the inboard side edge part of an inner ring | wheel, and the shoulder part of an outer joint member. 本発明における第五の実施形態で、軸受部に組み付けられた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適用例を示す縦断面図である。In 5th embodiment in this invention, it is a longitudinal cross-sectional view which shows the application example which interposed the plate assembled | attached to the bearing part between the caulking part of a hub ring, and the shoulder part of an outer joint member. 本発明における第六の実施形態で、軸受部に組み付けられた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適用例を示す縦断面図である。It is a longitudinal cross-sectional view which shows the application example which interposed the plate assembled | attached to the bearing part between the inboard side edge part of an inner ring | wheel, and the shoulder part of an outer joint member in 6th embodiment in 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
８０，８２，８４，８６ プレート
８１，８３，８５，８７ モリブデンコーティング層またはフッ素樹脂コーティング層
８２ａ，８４ａ，８６ａ 環状部
８２ｂ，８４ｂ，８６ｂ 筒状部 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 80, 82, 84, 86 Plate 81, 83, 85, 87 Molybdenum coating layer or fluororesin coating layer 82a, 84a, 86a Annular Part 82b, 84b, 86b cylindrical part

Claims (4)

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スプライン嵌合させ、前記内輪の端部を外側継手部材の肩部と対向させ、前記ステム部の端部に形成された雄ねじ部にナットを締め付けることによって等速自在継手をハブ輪に固定し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輪の端部との対向面間に、摺動特性の優れたコーティング層が形成され、かつ、板厚が０．５ｍｍ〜２ｍｍを有するステンレス鋼製のプレートを介在させ、軸力により面圧が加わるプレートの耐力を２０５Ｎ／ｍｍ2以上とし、前記プレートは、外側継手部材の肩部と内輪の端部との二つの対向面間に介在する環状部と、その環状部の周縁を軸方向に延在して前記内輪の端部に嵌合させた筒状部とで構成され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 The constant velocity universal joint is fixed to the hub wheel by fitting the part with a spline, making the end of the inner ring face the shoulder of the outer joint member, and tightening the nut to the male thread formed at the end of the stem part. In the drive wheel bearing device, a coating layer having excellent sliding characteristics is formed between the opposing surfaces of the shoulder portion of the outer joint member and the end portion of the inner ring, and the plate thickness is 0.5 mm to 2 mm. A stainless steel plate with The yield strength of the plate surface pressure is applied to the 205N / mm 2 or more, the plate includes an annular portion interposed between the two opposing surfaces of the shoulder portion of the outer joint member and the inner ring of the end, the peripheral edge of the annular portion A drive wheel bearing device comprising: a cylindrical portion extending in an axial direction and fitted to an end portion of the inner ring . 前記プレートにおけるコーティング層をモリブデンコーティング層とした請求項１に記載の駆動車輪用軸受装置。   The drive wheel bearing device according to claim 1, wherein the coating layer on the plate is a molybdenum coating layer. 前記プレートにおけるコーティング層をフッ素樹脂コーティング層とした請求項１に記載の駆動車輪用軸受装置。   The drive wheel bearing device according to claim 1, wherein the coating layer on the plate is a fluororesin coating layer. 前記プレートにおけるコーティング層の膜厚を２μｍ〜３０μｍ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。   The bearing apparatus for drive wheels as described in any one of Claims 1-3 which set the film thickness of the coating layer in the said plate to 2 micrometers-30 micrometers.
JP2008078994A 2008-03-25 2008-03-25 Drive wheel bearing device Active JP5594505B2 (en)

Priority Applications (6)

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JP2008078994A JP5594505B2 (en) 2008-03-25 2008-03-25 Drive wheel bearing device
PCT/JP2009/054637 WO2009119313A1 (en) 2008-03-25 2009-03-11 Bearing device for driving wheel
US12/922,584 US8591118B2 (en) 2008-03-25 2009-03-11 Bearing device for driving wheel
CN200980110558.2A CN101980877B (en) 2008-03-25 2009-03-11 Bearing device for driving wheel
EP09725468.4A EP2263887B1 (en) 2008-03-25 2009-03-11 Bearing device for driving wheel
US14/050,685 US8783964B2 (en) 2008-03-25 2013-10-10 Bearing device for driving wheel

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JP2009286258A (en) * 2008-05-29 2009-12-10 Jtekt Corp Rolling bearing device
JP2011207375A (en) 2010-03-30 2011-10-20 Ntn Corp Bearing device for wheel containing in-wheel type motor
JP2012001010A (en) * 2010-06-14 2012-01-05 Ntn Corp Bearing device for wheel

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JP2004256106A (en) 1998-02-16 2004-09-16 Nsk Ltd Wheel driving axle unit
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JP4557223B2 (en) 2005-03-29 2010-10-06 Ｎｔｎ株式会社 Drive wheel bearing device
JP2007076465A (en) 2005-09-13 2007-03-29 Ntn Corp Bearing device for driving wheel
JP2007276764A (en) * 2006-03-13 2007-10-25 Ntn Corp Bearing device for drive wheel
JP4952021B2 (en) 2006-03-30 2012-06-13 株式会社ジェイテクト Hub unit mounting structure
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