JP6860309B2 - Bearing device for wheels - Google Patents

Bearing device for wheels Download PDF

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JP6860309B2
JP6860309B2 JP2016174082A JP2016174082A JP6860309B2 JP 6860309 B2 JP6860309 B2 JP 6860309B2 JP 2016174082 A JP2016174082 A JP 2016174082A JP 2016174082 A JP2016174082 A JP 2016174082A JP 6860309 B2 JP6860309 B2 JP 6860309B2
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hub
wheel
inner ring
ring
bearing device
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JP2018040408A (en
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大介 仲
大介 仲
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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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D1/108—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner 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
    • 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
    • F16C35/0635—Fixing them on the shaft the bore of the inner ring being of special non-cylindrical shape which co-operates with a complementary shape on the shaft, e.g. teeth, polygonal sections
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member

Description

本発明は車輪用軸受装置に関する。詳しくはドライブシャフトとのガタを小さくした駆動輪用の車輪用軸受装置に関する。 The present invention relates to a wheel bearing device. More specifically, the present invention relates to a wheel bearing device for drive wheels with less play with the drive shaft.

従来、自動車等の懸架装置において車輪を回転自在に支持する車輪用軸受装置が知られている。車輪用軸受装置は、車輪に接続されるハブ輪が転動体を介して外輪に回転自在に支持されている。車輪用軸受装置は、車両のナックルに外輪の取り付けフランジを介して固定されている。つまり、車輪用軸受装置は、外輪が車両のナックルに固定された状態で車輪が接続されているハブ輪を回転自在に支持している。また、駆動輪用の車輪用軸受装置は、ハブ輪に車両のドライブシャフトがスプライン嵌合されている。さらに、駆動輪用の車輪用軸受装置は、ナットの締め付けによりドライブシャフトの肩部（段差面）にハブ輪の端面が押し付けられてドライブシャフトに固定されている。駆動輪用の車輪用軸受装置は、ドライブシャフトからの回転力の伝達によってハブ輪が回転駆動されるように構成されている。 Conventionally, a wheel bearing device that rotatably supports a wheel in a suspension device such as an automobile has been known. In the wheel bearing device, the hub ring connected to the wheel is rotatably supported by the outer ring via a rolling element. The wheel bearing device is fixed to the knuckle of the vehicle via the mounting flange of the outer ring. That is, the wheel bearing device rotatably supports the hub wheel to which the wheel is connected with the outer ring fixed to the knuckle of the vehicle. Further, in the wheel bearing device for drive wheels, the drive shaft of the vehicle is spline-fitted to the hub wheel. Further, the wheel bearing device for the drive wheel is fixed to the drive shaft by pressing the end surface of the hub wheel against the shoulder portion (step surface) of the drive shaft by tightening the nut. The wheel bearing device for drive wheels is configured so that the hub wheels are rotationally driven by the transmission of rotational force from the drive shaft.

このような車輪用軸受装置において、ドライブシャフトとハブ輪とのスプライン嵌合に隙間がある場合、車両の急発進等による大きな回転力によってスプラインシャフトが回転されるとドライブシャフトの肩部とハブ輪の端面との間に急激なスリップ（すべり）が生じ、スティックスリップ音が発生する可能性があった。そこで、ドライブシャフトと車輪用軸受装置とを接続する際、ドライブシャフトの肩部とハブ輪の端面との間にスティックスリップ音の発生を防止するためのプレートを挟み込む技術が知られている。例えば、特許文献１に記載の如くである。 In such a wheel bearing device, if there is a gap in the spline fitting between the drive shaft and the hub wheel, the shoulder of the drive shaft and the hub wheel will be rotated when the spline shaft is rotated by a large rotational force due to a sudden start of the vehicle or the like. There was a possibility that a sudden slip (slip) occurred between the wheel and the end face of the wheel, and a stick slip sound was generated. Therefore, there is known a technique of sandwiching a plate for preventing the generation of stick slip sound between the shoulder portion of the drive shaft and the end surface of the hub wheel when connecting the drive shaft and the wheel bearing device. For example, as described in Patent Document 1.

特許文献１に記載の車輪用軸受装置は、表面にショットピーニング処理を施した析出硬化系ステンレスに二硫化モリブデンからなる固体潤滑被膜を形成させたプレートをドライブシャフトの肩部とハブ輪の端面との間に組み込まれている。このように構成することで、車輪用軸受装置は、ドライブシャフトの肩部とハブ輪の端面との間に相対的な移動が生じてもプレートの潤滑機能により急激なスリップが緩和されてスティックスリップ音の発生が抑制される。しかし、特許文献１の技術では、表面に特殊な加工を施したプレートを作成して組み込む必要がある。また、経年的な摩耗により個体潤滑被膜が失われた場合、スティックスリップ音が再び発生する可能性があった。 In the wheel bearing device described in Patent Document 1, a plate in which a solid lubricating film made of molybdenum disulfide is formed on a precipitation hardening stainless steel whose surface is shot peened is used as a shoulder portion of a drive shaft and an end surface of a hub wheel. It is built in between. With this configuration, the wheel bearing device can alleviate sudden slip due to the lubrication function of the plate even if relative movement occurs between the shoulder of the drive shaft and the end face of the hub wheel, and stick slip. Sound generation is suppressed. However, in the technique of Patent Document 1, it is necessary to prepare and incorporate a plate having a specially processed surface. In addition, if the solid lubricating film was lost due to aging wear, stick-slip noise could occur again.

特開２０１３−１６６４８７号公報Japanese Unexamined Patent Publication No. 2013-166487

本発明は以上の如き状況に鑑みてなされたものであり、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる車輪用軸受装置の提供を目的とする。 The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a wheel bearing device capable of preventing the generation of stick-slip noise for a long period of time without adding special parts.

即ち、車輪用軸受装置においては、内周に複列の外側転走面が一体に形成された外方部材と、一端部に車輪を取り付けるための車輪取り付けフランジを一体に有し、外周に軸方向に延びる小径段部が形成され、内周にドライブシャフトがトルク伝達可能に係合される嵌合孔が形成されるハブ輪、およびこのハブ輪の小径段部に圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、この内方部材と前記外方部材のそれぞれの転走面間に転動自在に収容された複列の転動体と、を備えた車輪用軸受装置において、前記小径段部と前記小径段部が圧入される前記内輪の嵌合孔とがそれぞれテーパ形状に形成されるものである。 That is, in the wheel bearing device, an outer member having a double row of outer rolling surfaces integrally formed on the inner circumference and a wheel mounting flange for mounting the wheel at one end are integrally provided, and a shaft is provided on the outer circumference. A hub wheel having a small diameter step extending in the direction and a fitting hole formed in the inner circumference to engage a drive shaft so as to transmit torque, and at least one inner ring press-fitted into the small diameter step of the hub wheel. An inner member having a double-row inner rolling surface facing the outer rolling surface of the double-row on the outer periphery thereof, and rolling between the inner member and each rolling surface of the outer member. In a wheel bearing device including a movably housed double-row rolling element, the small-diameter step portion and the fitting hole of the inner ring into which the small-diameter step portion is press-fitted are each formed in a tapered shape. It is a thing.

車輪用軸受装置においては、前記小径段部と前記内輪との嵌合において小径側端の締め代が最も大きくなるようにテーパ形状が形成されるものである。 In the wheel bearing device, a tapered shape is formed so that the tightening allowance at the small diameter side end is maximized when the small diameter step portion and the inner ring are fitted.

車輪用軸受装置においては、前記小径段部と前記内輪との嵌合においてすべての嵌合部分に締め代が生じるようにテーパ形状が形成されるものである。 In the wheel bearing device, a tapered shape is formed so that a tightening allowance is generated in all the fitting portions when the small diameter step portion and the inner ring are fitted.

車輪用軸受装置においては、前記小径段部と前記内輪とのテーパ形状の少なくとも一部が、前記ハブ輪においてドライブシャフトが係合している部分と径方向視で重複する位置に形成されるものである。 In a wheel bearing device, at least a part of the tapered shape of the small diameter step portion and the inner ring is formed at a position where the hub wheel overlaps with the portion where the drive shaft is engaged in the radial direction. Is.

本発明の効果として、以下に示すような効果を奏する。 As the effect of the present invention, the following effects are exhibited.

即ち、本発明によれば、内輪にハブ輪がテーパ嵌合されることでハブ輪に発生する圧縮力によりハブ輪の嵌合孔が縮小されてハブ輪とドライブシャフトとの隙間が減少する。また、ドライブシャフトの肩部と内輪の端部との接触面積の増加に伴い、ドライブシャフトの肩部と内輪の端部との間の摩擦力が増大する。これにより、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる。 That is, according to the present invention, the fitting hole of the hub ring is reduced by the compressive force generated in the hub ring due to the taper fitting of the hub ring to the inner ring, and the gap between the hub ring and the drive shaft is reduced. Further, as the contact area between the shoulder portion of the drive shaft and the end portion of the inner ring increases, the frictional force between the shoulder portion of the drive shaft and the end portion of the inner ring increases. As a result, it is possible to prevent the generation of stick-slip noise for a long period of time without adding special parts.

本発明によれば、ハブ輪の嵌合孔のうちドライブシャフトの肩部と内輪の端部との接触面に最も近い部分が最も大きい圧縮力によって縮小されてドライブシャフトの肩部と内輪の端部との接触面に最も近い部分の隙間が最も減少する。これにより、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる。 According to the present invention, the portion of the fitting hole of the hub ring closest to the contact surface between the shoulder portion of the drive shaft and the end portion of the inner ring is reduced by the largest compressive force, and the shoulder portion of the drive shaft and the end of the inner ring are reduced. The gap in the portion closest to the contact surface with the portion is reduced most. As a result, it is possible to prevent the generation of stick-slip noise for a long period of time without adding special parts.

本発明によれば、ハブ輪の嵌合孔のうち内輪に嵌合されている部分の全体が圧縮力により縮小されてハブ輪とドライブシャフトとの隙間が減少する。これにより、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる。 According to the present invention, the entire portion of the fitting hole of the hub ring fitted to the inner ring is reduced by the compressive force to reduce the gap between the hub wheel and the drive shaft. As a result, it is possible to prevent the generation of stick-slip noise for a long period of time without adding special parts.

本発明によれば、内輪にハブ輪がテーパ嵌合されることでハブ輪に発生する圧縮力によりハブ輪の嵌合孔が縮小されてハブ輪とドライブシャフトとの隙間のうち少なくとも一部分が確実に減少する。これにより、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる。 According to the present invention, the fitting hole of the hub ring is reduced by the compressive force generated in the hub ring due to the taper fitting of the hub ring to the inner ring, and at least a part of the gap between the hub ring and the drive shaft is ensured. Decreases to. As a result, it is possible to prevent the generation of stick-slip noise for a long period of time without adding special parts.

本発明に係る車輪用軸受装置の一実施形態における全体構成を示す斜視図。The perspective view which shows the whole structure in one Embodiment of the wheel bearing device which concerns on this invention. 本発明に係る車輪用軸受装置の一実施形態における全体構成を示す断面図。FIG. 5 is a cross-sectional view showing an overall configuration of an embodiment of a wheel bearing device according to the present invention. 本発明に係る車輪用軸受装置の一実施形態におけるドライブシャフトが嵌合された状態を示す断面図。FIG. 5 is a cross-sectional view showing a state in which a drive shaft is fitted according to an embodiment of a wheel bearing device according to the present invention. （ａ）本発明に係る車輪用軸受装置一実施形態におけるハブ輪のテーパ形状を示す断面図、（ｂ）同じく内輪のテーパ形状を示す断面図。(A) A cross-sectional view showing a tapered shape of a hub ring according to an embodiment of a wheel bearing device according to the present invention, and (b) a cross-sectional view showing a tapered shape of an inner ring. 本発明に係る車輪用軸受装置の一実施形態におけるハブ輪のテーパ形状部分と外輪のテーパ形状部分とが接触した状態を示す拡大部分断面図、（ｂ）同じくハブ輪に内輪がドライブシャフトによって圧入されている過程を示す拡大部分断面図。An enlarged partial cross-sectional view showing a state in which the tapered portion of the hub ring and the tapered portion of the outer ring are in contact with each other in one embodiment of the wheel bearing device according to the present invention. (B) Similarly, the inner ring is press-fitted into the hub ring by a drive shaft. Enlarged partial cross-sectional view showing the process being carried out. （ａ）本発明に係る車輪用軸受装置の一実施形態におけるハブ輪に内輪が圧入されていない場合のハブ輪のセレーションとドライブシャフトのセレーションとが係合している状態を示す拡大部分断面図、（ｂ）同じくハブ輪に内輪が圧入されている場合のハブ輪のセレーションとドライブシャフトのセレーションとが係合している状態を示す拡大部分断面図。(A) Enlarged partial cross-sectional view showing a state in which the serrations of the hub wheels and the serrations of the drive shaft are engaged when the inner ring is not press-fitted into the hub wheels according to the embodiment of the wheel bearing device according to the present invention. , (B) Similarly, an enlarged partial cross-sectional view showing a state in which the serrations of the hub wheels and the serrations of the drive shaft are engaged when the inner ring is press-fitted into the hub wheels.

以下に、図１と図２とを用いて、本発明に係る車輪用軸受装置の一実施形態である車輪用軸受装置１について説明する。 Hereinafter, the wheel bearing device 1 which is an embodiment of the wheel bearing device according to the present invention will be described with reference to FIGS. 1 and 2.

図１に示すように、車輪用軸受装置１は、自動車等の車両の懸架装置において車輪を回転自在に支持するものである。車輪用軸受装置１は、外方部材である外輪２、内方部材を構成するハブ輪３、内方部材を構成する内輪４、転動列である二列の一側ボール列５ａ（図２参照）、他側ボール列５ｂ（図２参照）、一側（インナー側）シール部材６、他側（アウター側）シール部材７（図２参照）を具備する。 As shown in FIG. 1, the wheel bearing device 1 rotatably supports wheels in a suspension device for a vehicle such as an automobile. The wheel bearing device 1 includes an outer ring 2 which is an outer member, a hub ring 3 which constitutes an inner member, an inner ring 4 which constitutes an inner member, and a two-row one-side ball row 5a which is a rolling row (FIG. 2). (See), the other side ball row 5b (see FIG. 2), one side (inner side) sealing member 6, and the other side (outer side) sealing member 7 (see FIG. 2).

図２に示すように、外方部材である外輪２は、内方部材（ハブ輪３と内輪４）を支持するものである。外輪２は、略円筒状に形成されたＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で構成されている。外輪２の一側（インナー側）端部には、一側シール部材６が嵌合可能な一側開口部２ａが形成されている。外輪２の他側（アウター側）端部には、他側シール部材７が嵌合可能な外方部材開口部である他側開口部２ｂが形成されている。 As shown in FIG. 2, the outer ring 2 which is an outer member supports the inner member (hub ring 3 and inner ring 4). The outer ring 2 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C formed in a substantially cylindrical shape. A one-side opening 2a into which the one-side seal member 6 can be fitted is formed at one side (inner side) end of the outer ring 2. At the other side (outer side) end of the outer ring 2, an other side opening 2b, which is an outer member opening into which the other side seal member 7 can be fitted, is formed.

外輪２の内周面には、環状に形成されている一側の外側転走面２ｃと他側の外側転走面２ｄとが周方向に互いに平行になるように形成されている。一側の外側転走面２ｃと他側の外側転走面２ｄとのピッチ円直径は、等しい大きさに構成されている。なお、一側の外側転走面２ｃと他側の外側転走面２ｄとのピッチ円直径は、異なる大きさに構成してもよい。一側の外側転走面２ｃと他側の外側転走面２ｄとには、高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲とする硬化層が形成されている。外輪２の外周面には、図示しない懸架装置のナックルに取り付けられるための車体取り付けフランジ２ｅが一側開口部２ａの近傍に一体に形成されている。車体取り付けフランジ２ｅは、外輪２の一側の外側転走面２ｃに対向する部分を含む範囲に形成されている。 The inner peripheral surface of the outer ring 2 is formed so that the outer rolling surface 2c on one side and the outer rolling surface 2d on the other side, which are formed in an annular shape, are parallel to each other in the circumferential direction. The pitch circle diameters of the outer rolling surface 2c on one side and the outer rolling surface 2d on the other side are configured to have the same size. The pitch circle diameters of the outer rolling surface 2c on one side and the outer rolling surface 2d on the other side may be configured to have different sizes. A hardened layer having a surface hardness in the range of 58 to 64 HRC is formed on the outer rolling surface 2c on one side and the outer rolling surface 2d on the other side by induction hardening. On the outer peripheral surface of the outer ring 2, a vehicle body mounting flange 2e for mounting on a knuckle of a suspension device (not shown) is integrally formed in the vicinity of the one-side opening 2a. The vehicle body mounting flange 2e is formed in a range including a portion facing the outer rolling surface 2c on one side of the outer ring 2.

内方部材を構成するハブ輪３は、図示しない車両の車輪を回転自在に支持するものである。ハブ輪３は、円筒状に形成されたＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で構成されている。ハブ輪３の一側端部（インナー側）には、一側端から軸方向に所定の範囲だけ外径が小さい部分である小径段部３ａが形成されている。つまり、小径段部３ａの一側端は、ハブ輪３の一側端であり、小径段部３ａの他側端には、段差３ｂが形成されている。小径段部３ａは、その外周面がテーパ状に形成されている。ハブ輪３の他側端部（アウター側）には、車輪を取り付けるための車輪取り付けフランジ３ｃが一体的に形成されている。ハブ輪３の他側（車輪取り付けフランジ３ｃ側）の外周面には、周方向に環状の内側転走面３ｄと環状のシール摺動面３ｅとが形成されている。ハブ輪３は、他側に形成されている内側転走面３ｄが外輪２の他側の外側転走面２ｄに対向するように配置されている。 The hub wheel 3 constituting the inner member rotatably supports a wheel of a vehicle (not shown). The hub ring 3 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C formed in a cylindrical shape. A small diameter step portion 3a, which is a portion having a small outer diameter by a predetermined range in the axial direction from the one side end, is formed on one side end portion (inner side) of the hub ring 3. That is, one side end of the small diameter step portion 3a is one side end of the hub ring 3, and a step 3b is formed at the other side end of the small diameter step portion 3a. The outer peripheral surface of the small diameter step portion 3a is formed in a tapered shape. A wheel mounting flange 3c for mounting a wheel is integrally formed at the other end (outer side) of the hub wheel 3. On the outer peripheral surface of the other side (wheel mounting flange 3c side) of the hub wheel 3, an annular inner rolling surface 3d and an annular seal sliding surface 3e are formed in the circumferential direction. The hub ring 3 is arranged so that the inner rolling surface 3d formed on the other side faces the outer rolling surface 2d on the other side of the outer ring 2.

ハブ輪３は、一側の小径段部３ａから他側の内側転走面３ｄまでを高周波焼入れにより表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。これにより、ハブ輪３は、車輪取り付けフランジ３ｃに付加される回転曲げ荷重に対して充分な機械的強度を有し、ハブ輪３の耐久性が向上する。車輪取り付けフランジ３ｃには、円周等配位置にハブボルト３ｆが設けられている。ハブ輪３の内周は、トルク伝達用のセレーション３ｈ（またはスプライン）が形成されているハブ輪嵌合孔３ｇとして構成されている。 The surface hardness of the hub ring 3 is hardened in the range of 58 to 64 HRC by induction hardening from the small diameter step portion 3a on one side to the inner rolling surface 3d on the other side. As a result, the hub wheel 3 has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 3c, and the durability of the hub wheel 3 is improved. The wheel mounting flange 3c is provided with hub bolts 3f at positions that are evenly distributed around the circumference. The inner circumference of the hub wheel 3 is configured as a hub wheel fitting hole 3g in which a serration 3h (or spline) for torque transmission is formed.

内輪４は、転動列である一側ボール列５ａと他側ボール列５ｂとに予圧を与えるものである。内輪４は、円筒状に形成されている。内輪４は、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。内輪４の外周面には、周方向に環状の内側転走面４ａが形成されている。内輪４の内周は、ハブ輪３の小径段部３ａが圧入により嵌合される内輪４の嵌合孔である内輪嵌合孔４ｂとして構成されている。内輪４は、ハブ輪３の小径段部３ａに内輪嵌合孔４ｂが嵌合されることでハブ輪３の一側に内側転走面４ａを構成している。内輪４は、内輪嵌合孔４ｂの内周面がテーパ状に形成されている。内輪４は、内側転走面４ａが外輪２の一側の外側転走面２ｃに対向するように配置されている。 The inner ring 4 applies a preload to the one-side ball row 5a and the other-side ball row 5b, which are rolling rows. The inner ring 4 is formed in a cylindrical shape. The inner ring 4 is made of high carbon chrome bearing steel such as SUJ2, and is hardened to the core in the range of 58 to 64 HRC by quenching. An annular inner rolling surface 4a is formed on the outer peripheral surface of the inner ring 4 in the circumferential direction. The inner circumference of the inner ring 4 is configured as an inner ring fitting hole 4b, which is a fitting hole of the inner ring 4 into which the small diameter step portion 3a of the hub ring 3 is press-fitted. The inner ring 4 has an inner rolling surface 4a formed on one side of the hub ring 3 by fitting the inner ring fitting hole 4b into the small diameter step portion 3a of the hub ring 3. The inner ring 4 has a tapered inner peripheral surface of the inner ring fitting hole 4b. The inner ring 4 is arranged so that the inner rolling surface 4a faces the outer rolling surface 2c on one side of the outer ring 2.

転動列である一側ボール列５ａと他側ボール列５ｂとは、ハブ輪３を回転自在に支持するものである。一側ボール列５ａと他側ボール列５ｂとは、転動体である複数のボールが保持器によって環状に保持されている。一側ボール列５ａと他側ボール列５ｂとは、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。一側ボール列５ａは、内輪４に形成されている内側転走面４ａと、それに対向している外輪２の一側の外側転走面２ｃとの間に転動自在に挟まれている。他側ボール列５ｂは、ハブ輪３に形成されている内側転走面３ｄと、それに対向している外輪２の他側の外側転走面２ｄとの間に転動自在に挟まれている。つまり、一側ボール列５ａと他側ボール列５ｂとは、外輪２に対してハブ輪３と内輪４とを回転自在に支持している。 The one-side ball row 5a and the other-side ball row 5b, which are rolling rows, rotatably support the hub wheel 3. In the one-side ball row 5a and the other-side ball row 5b, a plurality of balls, which are rolling elements, are held in an annular shape by a cage. The one-side ball row 5a and the other-side ball row 5b are made of high-carbon chrome bearing steel such as SUJ2, and are hardened to the core in the range of 58 to 64 HRC by quenching. The one-side ball row 5a is rotatably sandwiched between the inner rolling surface 4a formed on the inner ring 4 and the outer rolling surface 2c on one side of the outer ring 2 facing the inner rolling surface 4a. The other side ball row 5b is rotatably sandwiched between the inner rolling surface 3d formed on the hub ring 3 and the outer rolling surface 2d on the other side of the outer ring 2 facing the inner rolling surface 3d. .. That is, the one-side ball row 5a and the other-side ball row 5b rotatably support the hub ring 3 and the inner ring 4 with respect to the outer ring 2.

車輪用軸受装置１は、外輪２とハブ輪３と内輪４と一側ボール列５ａと他側ボール列５ｂとから複列アンギュラ玉軸受が構成されている。なお、本実施形態において、車輪用軸受装置１には、複列アンギュラ玉軸受が構成されているがこれに限定されるものではなく、複列円錐ころ軸受等で構成されていても良い。 The wheel bearing device 1 is composed of an outer ring 2, a hub ring 3, an inner ring 4, a ball row 5a on one side, and a ball row 5b on the other side to form a double row angular contact ball bearing. In the present embodiment, the wheel bearing device 1 is configured with a double-row angular contact ball bearing, but the present invention is not limited to this, and a double-row conical roller bearing or the like may be used.

一側（インナー側）シール部材６は、外輪２と内輪４との隙間を塞ぐものである。一側シール部材６は、略円筒状のシール板と略円筒状のスリンガとを具備する。一側シール部材６は、フェライト系ステンレス鋼板（ＪＩＳ規格のＳＵＳ４３０系等）等から構成されているシール板に、ＮＢＲ（アクリロニトリル−ブタジエンゴム）等の合成ゴムからなる複数の一側シールリップが加硫接着されている。スリンガは、シール板と同等の鋼板から構成されている。一側シール部材６は、シール板が外輪２の一側開口部２ａに嵌合され、スリンガの円筒部分が内輪４に嵌合され、パックシールを構成している。スリンガは、その鍔部分が外側（インナー側）に向くようにして内輪４に固定されている。一側シール部材６は、シール板の一側シールリップが油膜を介してスリンガと接触することでスリンガに対して摺動可能に構成されている。これにより、一側シール部材６は、外輪２の一側開口部２ａからの潤滑グリースの漏れ、および外部からの雨水や粉塵等の侵入を防止する。 The one side (inner side) seal member 6 closes the gap between the outer ring 2 and the inner ring 4. The one-side seal member 6 includes a substantially cylindrical seal plate and a substantially cylindrical slinger. The one-side sealing member 6 is a sealing plate made of a ferrite-based stainless steel plate (JIS standard SUS430 series, etc.) and a plurality of one-sided sealing lips made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber). It is vulcanized. The slinger is composed of a steel plate equivalent to a sealing plate. In the one-side seal member 6, the seal plate is fitted into the one-side opening 2a of the outer ring 2, and the cylindrical portion of the slinger is fitted into the inner ring 4 to form a pack seal. The slinger is fixed to the inner ring 4 so that its collar portion faces outward (inner side) . The one- side seal member 6 is configured to be slidable with respect to the slinger when the one-side seal lip of the seal plate comes into contact with the slinger via an oil film. As a result, the one-side sealing member 6 prevents the lubricating grease from leaking from the one-side opening 2a of the outer ring 2 and the intrusion of rainwater, dust, and the like from the outside.

他側（アウター側）シール部材７は、外輪２とハブ輪３との隙間を塞ぐものである。他側シール部材７は、ニトリルゴム等の合成ゴムからなる複数の他側シールリップが、加硫接着によって略円筒状に形成された芯金に一体に接合されている。他側シール部材７は、外輪２の他側開口部２ｂに円筒部分が嵌合され、ハブ輪３の外周面に複数の他側シールリップが接触している。他側シール部材７は、他側シールリップが油膜を介してハブ輪３の外周面と接触することでハブ輪３に対して摺動可能に構成されている。これにより、他側シール部材７は、外輪２の他側開口部２ｂからの潤滑グリースの漏れ、および外部からの雨水や粉塵等の侵入を防止する。 The other side (outer side) seal member 7 closes the gap between the outer ring 2 and the hub ring 3. Other side sealing member 7, a plurality of the other seal lip made of a synthetic rubber such as nitrile rubber, is integrally joined to the metal core which is formed in a substantially cylindrical shape by vulcanization bonding. The other-side seal member 7 has a cylindrical portion fitted in the other-side opening 2b of the outer ring 2, and a plurality of other-side seal lips are in contact with the outer peripheral surface of the hub ring 3. The other-side seal member 7 is configured to be slidable with respect to the hub ring 3 when the other-side seal lip comes into contact with the outer peripheral surface of the hub ring 3 via an oil film. As a result, the other side sealing member 7 prevents the lubricating grease from leaking from the other side opening 2b of the outer ring 2 and the intrusion of rainwater, dust, etc. from the outside.

このように構成される車輪用軸受装置１は、外輪２とハブ輪３と内輪４と一側ボール列５ａと他側ボール列５ｂとから複列アンギュラ玉軸受が構成され、ハブ輪３が一側ボール列５ａと他側ボール列５ｂを介して外輪２に回転自在に支持されている。また、車輪用軸受装置１は、外輪２の一側開口部２ａと内輪４との隙間を一側シール部材６で塞がれ、外輪２の他側開口部２ｂとハブ輪３との隙間を他側シール部材７で塞がれている。これにより、車輪用軸受装置１は、内部からの潤滑グリースの漏れ、および外部からの雨水や粉塵等の侵入を防止しつつ外輪２に支持されているハブ輪３が回転可能に構成されている。 In the wheel bearing device 1 configured in this way, a double row angular contact ball bearing is formed from the outer ring 2, the hub wheel 3, the inner ring 4, the one-side ball row 5a, and the other-side ball row 5b, and the hub wheel 3 is one. It is rotatably supported by the outer ring 2 via the side ball row 5a and the other side ball row 5b. Further, in the wheel bearing device 1, the gap between the one-side opening 2a of the outer ring 2 and the inner ring 4 is closed by the one-side sealing member 6, and the gap between the other-side opening 2b of the outer ring 2 and the hub ring 3 is closed. It is closed by the other side seal member 7. As a result, the wheel bearing device 1 is configured so that the hub wheel 3 supported by the outer ring 2 can rotate while preventing leakage of lubricating grease from the inside and intrusion of rainwater, dust, etc. from the outside. ..

図３に示すように、車輪用軸受装置１には、ハブ輪３のハブ輪嵌合孔３ｇに一側（インナー側）端部側からトルク伝達用のドライブシャフト１００が挿入されている。車輪用軸受装置１は、ドライブシャフト１００のセレーション１００ａ（またはスプライン）とハブ輪嵌合孔３ｇのセレーション３ｈとが係合されている。さらに、車輪用軸受装置１は、ドライブシャフト１００にナットが締め込まれることでハブ輪３と内輪４とを含む内方部材がドライブシャフト１００に固定されている。この際、車輪用軸受装置１は、ドライブシャフト１００に発生している軸力により内輪４の一側端面がドライブシャフト１００の肩部１００ｂに押し付けれている。これにより、車輪用軸受装置１は、ドライブシャフト１００の肩部１００ｂによって内輪４がハブ輪３の他側（アウター側）に向かって押圧されて小径段部３ａに圧入嵌合されている。内輪４は、他側端が小径段部３ａの段差３ｂに接触することでハブ輪３に対する軸方向の位置が定まる。 As shown in FIG. 3, in the wheel bearing device 1, a drive shaft 100 for torque transmission is inserted into the hub wheel fitting hole 3g of the hub wheel 3 from one side (inner side) end side. In the wheel bearing device 1, the serration 100a (or spline) of the drive shaft 100 and the serration 3h of the hub wheel fitting hole 3g are engaged with each other. Further, in the wheel bearing device 1, the inner member including the hub wheel 3 and the inner ring 4 is fixed to the drive shaft 100 by tightening a nut on the drive shaft 100. At this time, in the wheel bearing device 1, one side end surface of the inner ring 4 is pressed against the shoulder portion 100b of the drive shaft 100 by the axial force generated in the drive shaft 100. As a result, in the wheel bearing device 1, the inner ring 4 is pressed toward the other side (outer side) of the hub wheel 3 by the shoulder portion 100b of the drive shaft 100, and is press-fitted into the small diameter step portion 3a. The position of the inner ring 4 in the axial direction with respect to the hub wheel 3 is determined when the other side end contacts the step 3b of the small diameter step portion 3a.

次に、図４から図６を用いて、ハブ輪３と内輪４とのテーパ形状および嵌合状態について詳細に説明する。 Next, the tapered shape and the fitted state of the hub ring 3 and the inner ring 4 will be described in detail with reference to FIGS. 4 to 6.

図４（ａ）に示すように、ハブ輪３の小径段部３ａは、外周面がテーパ角αのテーパ形状に形成されている。小径段部３ａは、段差３ｂからハブ輪３の一側（インナー側）端に向かうにつれて外径が小さくなる円錐台状に形成されている。また、小径段部３ａは、径方向視で少なくとも一部がハブ輪３の内周に形成されているセレーション３ｈと重複する位置に形成されている。つまり、小径段部３ａの段差３ｂは、セレーション３ｈの一側端よりも長さＸだけ他側（アウター側）に形成されている。 As shown in FIG. 4A, the outer peripheral surface of the small diameter step portion 3a of the hub ring 3 is formed in a tapered shape having a taper angle α. The small diameter step portion 3a is formed in a truncated cone shape in which the outer diameter decreases toward one side (inner side) end of the hub ring 3 from the step 3b. Further, the small diameter step portion 3a is formed at a position overlapping with the serration 3h formed on the inner circumference of the hub ring 3 at least in part in the radial direction. That is, the step 3b of the small diameter step portion 3a is formed on the other side (outer side) by the length X from one side end of the serration 3h.

図４（ｂ）に示すように、内輪４の内輪嵌合孔４ｂは、アウター側（他側）からインナー側（一側）に向かうテーパ角βのテーパ形状に形成されている。つまり、内輪４の内輪嵌合孔４ｂは、ハブ輪３の段差３ｂ側からハブ輪３の一側端に向かうにつれて内径が小さくなる円錐台状の孔に形成されている。これにより、内輪４の一側端面の面積は、一側に向かうにつれて肉厚が厚くなり、全域に渡って他側の内径からなるテーパ形状でない嵌合孔が形成されている場合の一側端面の面積よりも大きくなる。内輪４は、ハブ輪３の小径段部３ａよりも軸方向長さが大きくなるように形成されている。すなわち、内輪４は、他側端が小径段部３ａの段差３ｂに接触する状態で嵌合されてもハブ輪３の一側端よりも軸方向に突出するように構成されている。 As shown in FIG. 4B, the inner ring fitting hole 4b of the inner ring 4 is formed in a tapered shape having a taper angle β from the outer side (other side) to the inner side (one side). That is, the inner ring fitting hole 4b of the inner ring 4 is formed in a truncated cone-shaped hole whose inner diameter decreases toward one side end of the hub ring 3 from the step 3b side of the hub ring 3. As a result, the area of the one-side end surface of the inner ring 4 becomes thicker toward one side, and the one-side end surface when a non-tapered fitting hole consisting of the inner diameter of the other side is formed over the entire area. Is larger than the area of. The inner ring 4 is formed so as to have an axial length larger than that of the small diameter step portion 3a of the hub ring 3. That is, the inner ring 4 is configured to protrude in the axial direction from one side end of the hub ring 3 even if the other side end is fitted in a state of being in contact with the step 3b of the small diameter step portion 3a.

ハブ輪３の小径段部３ａのテーパ形状と内輪４の内輪嵌合孔４ｂのテーパ形状とは、小径段部３ａの全体が内輪４によって径方向内側に圧縮されるように、小径段部３ａの外周面の全面に内輪４の内輪嵌合孔４ｂの内周面が接触するように形成されている。すなわち、ハブ輪３の小径段部３ａのテーパ形状と内輪４の内輪嵌合孔４ｂのテーパ形状とは、小径段部３ａの外周面の所定位置で所定の締め代が生じるように小径段部３ａのテーパ角α、内輪嵌合孔４ｂのテーパ角βおよび基準径が設定されている。加えて、小径段部３ａのテーパ形状と内輪嵌合孔４ｂのテーパ形状とは、小径段部３ａのテーパ形状の小径側端の締め代が最も大きくなるようにテーパ角α、テーパ角βおよび基準径が設定されている。つまり、小径段部３ａのテーパ角αは、内輪嵌合孔４ｂのテーパ角βより小さく設定されている。なお、テーパ角αおよびテーパ角βは、圧入嵌合時の抵抗等を鑑みて２０°以下の範囲で設定されている。 The tapered shape of the small diameter step portion 3a of the hub ring 3 and the tapered shape of the inner ring fitting hole 4b of the inner ring 4 are such that the entire small diameter step portion 3a is compressed inward in the radial direction by the inner ring 4 so that the small diameter step portion 3a The inner peripheral surface of the inner ring fitting hole 4b of the inner ring 4 is formed so as to come into contact with the entire outer peripheral surface of the inner ring 4. That is, the tapered shape of the small diameter step portion 3a of the hub ring 3 and the tapered shape of the inner ring fitting hole 4b of the inner ring 4 are such that a predetermined tightening allowance is generated at a predetermined position on the outer peripheral surface of the small diameter step portion 3a. The taper angle α of 3a, the taper angle β of the inner ring fitting hole 4b, and the reference diameter are set. In addition, the tapered shape of the small diameter step portion 3a and the tapered shape of the inner ring fitting hole 4b are the taper angle α, the taper angle β, and the taper angle β and the taper angle β so that the tightening allowance at the small diameter side end of the tapered shape of the small diameter step portion 3a is maximized. The reference diameter is set. That is, the taper angle α of the small diameter step portion 3a is set to be smaller than the taper angle β of the inner ring fitting hole 4b. The taper angle α and the taper angle β are set in a range of 20 ° or less in consideration of resistance at the time of press-fitting and fitting.

図５（ａ）に示すように、ハブ輪３の小径段部３ａに嵌合されている内輪４がドライブシャフト１００の肩部１００ｂによって押圧されていない場合、小径段部３ａと内輪４とは、それぞれのテーパ形状によって、小径段部３ａの外周面と内輪嵌合孔４ｂの内周面のうち小径側端の当たりが最も大きい状態で嵌合されている。つまり、小径段部３ａと内輪４とは、一側（インナー側）である小径側端が最も強く接触し（黒塗矢印参照）、他側（アウター側）である大径側端に隙間Ｇ１が生じている状態で嵌合されている。 As shown in FIG. 5A, when the inner ring 4 fitted to the small diameter step portion 3a of the hub ring 3 is not pressed by the shoulder portion 100b of the drive shaft 100, the small diameter step portion 3a and the inner ring 4 are different from each other. According to each tapered shape, the outer peripheral surface of the small diameter step portion 3a and the inner peripheral surface of the inner ring fitting hole 4b are fitted in a state where the contact between the small diameter side end is the largest. That is, the small diameter step portion 3a and the inner ring 4 have the strongest contact with the small diameter side end on one side (inner side) (see the black arrow), and the gap G1 with the large diameter side end on the other side (outer side). Is fitted in a state where

図５（ｂ）に示すように、ハブ輪３の小径段部３ａに嵌合されている内輪４がドライブシャフト１００（薄墨部分参照）の肩部１００ｂによって大径側に向かって押圧されている場合（白塗矢印参照）、小径段部３ａは、内輪４によって小径側端が径方向内側に向かって圧縮される。同時に、内輪嵌合孔４ｂは、小径側端が径方向外側に向かって膨張される（黒塗矢印参照）。小径段部３ａは、肩部１００ｂの押圧により内輪４が大径側に向かって嵌合されるにつれて、小径側端の圧縮量が増加するとともに内輪４によって押圧される範囲が大径側に向かって広がっていく。つまり、小径段部３ａは、内輪４が大径側に向かって圧入されるにつれて小径側から大径側に向かって順次圧縮される。 As shown in FIG. 5B, the inner ring 4 fitted to the small diameter step portion 3a of the hub ring 3 is pressed toward the large diameter side by the shoulder portion 100b of the drive shaft 100 (see the light ink portion). In the case (see the white-painted arrow), the small-diameter step portion 3a is compressed inward in the radial direction by the inner ring 4. At the same time, the small diameter side end of the inner ring fitting hole 4b is expanded toward the outside in the radial direction (see the black arrow). In the small diameter step portion 3a, as the inner ring 4 is fitted toward the large diameter side by pressing the shoulder portion 100b, the amount of compression at the small diameter side end increases and the range pressed by the inner ring 4 faces the large diameter side. And spread. That is, the small diameter step portion 3a is sequentially compressed from the small diameter side toward the large diameter side as the inner ring 4 is press-fitted toward the large diameter side.

小径段部３ａの段差３ｂと内輪４の他側端部とが接触している場合（図３参照）、小径段部３ａは、その外周面の全てが内輪嵌合孔４ｂの内周面と接触して、所定の締め代分だけ径方向内側に圧縮されている。この際、小径段部３ａは、小径側端が最も大きく圧縮されている。つまり、ハブ輪３は、ハブ輪嵌合孔３ｇのうち内輪４の小径側端である一側端面が接触しているドライブシャフト１００の肩部１００ｂに最も近接している部分が最も大きく径方向内側に圧縮されている。 When the step 3b of the small diameter step portion 3a is in contact with the other side end portion of the inner ring 4 (see FIG. 3), the entire outer peripheral surface of the small diameter step portion 3a is the inner peripheral surface of the inner ring fitting hole 4b. In contact with each other, they are compressed inward in the radial direction by a predetermined tightening allowance. At this time, the small-diameter step portion 3a is compressed most at the small-diameter side end. That is, in the hub ring 3, the portion of the hub ring fitting hole 3g that is closest to the shoulder portion 100b of the drive shaft 100 that is in contact with the one side end surface that is the small diameter side end of the inner ring 4 is the largest in the radial direction. It is compressed inward.

図６（ａ）に示すように、ハブ輪３のハブ輪嵌合孔３ｇが内輪４によって径方向内側に圧縮されていない場合、車輪用軸受装置１は、ドライブシャフト１００（薄墨部分参照）のセレーション１００ａとハブ輪３のセレーション３ｈとの間に隙間Ｇ２が生じている。 As shown in FIG. 6A, when the hub ring fitting hole 3g of the hub wheel 3 is not compressed inward in the radial direction by the inner ring 4, the wheel bearing device 1 is mounted on the drive shaft 100 (see the light ink portion). A gap G2 is formed between the serration 100a and the serration 3h of the hub wheel 3.

図６（ｂ）に示すように、ハブ輪３のハブ輪嵌合孔３ｇが内輪４の圧入嵌合によって径方向内側に圧縮されている場合（黒塗矢印参照）、ハブ輪３は、ハブ輪嵌合孔３ｇに形成されているセレーション３ｈの溝間隔および溝幅が縮小されている。さらに、ハブ輪３は、セレーション３ｈのうちドライブシャフト１００（薄墨部分参照）の肩部１００ｂ（図５（ｂ）参照）に最も近接している部分の溝間隔および溝幅が最も縮小されている。これにより、車輪用軸受装置１は、ドライブシャフト１００のセレーション１００ａとハブ輪３のセレーション３ｈとの隙間Ｇ２のうち少なくとも一部が内輪４の圧入嵌合によって減少されている。特に、車輪用軸受装置１は、隙間Ｇ２のうち肩部１００ｂに最も近接している部分が最も減少されている。従って、車輪用軸受装置１は、ドライブシャフト１００に大きな回転力が入力されてもドライブシャフト１００と内輪４のとの間でずれが発生し難い。これにより、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる。 As shown in FIG. 6B, when the hub ring fitting hole 3g of the hub ring 3 is compressed inward in the radial direction by press fitting of the inner ring 4 (see the black arrow), the hub ring 3 is a hub. The groove spacing and groove width of the serrations 3h formed in the ring fitting hole 3g are reduced. Further, in the hub wheel 3, the groove spacing and the groove width of the portion of the serration 3h closest to the shoulder portion 100b (see FIG. 5B) of the drive shaft 100 (see the light ink portion) are minimized. .. As a result, in the wheel bearing device 1, at least a part of the gap G2 between the serration 100a of the drive shaft 100 and the serration 3h of the hub wheel 3 is reduced by press-fitting the inner ring 4. In particular, in the wheel bearing device 1, the portion of the gap G2 closest to the shoulder portion 100b is most reduced. Therefore, in the wheel bearing device 1, even if a large rotational force is input to the drive shaft 100, deviation between the drive shaft 100 and the inner ring 4 is unlikely to occur. As a result, it is possible to prevent the generation of stick-slip noise for a long period of time without adding special parts.

さらに、車輪用軸受装置１は、ドライブシャフト１００の肩部１００ｂに接触している内輪４の小径側端面である一側端面の面積が、同一外径において内輪４にテーパ形状でない嵌合孔が形成されている場合の面積よりも大きい。これにより、車輪用軸受装置１は、内輪４の一側端部とドライブシャフト１００の肩部１００ｂとの間の摩擦力が増大するので、ドライブシャフト１００と内輪４との間で滑りが発生し難い。これにより、特殊な部品を追加することなく長期に渡ってスティックスリップ音の発生を防止することができる。 Further, in the wheel bearing device 1, the inner ring 4 has a fitting hole in which the area of one side end surface, which is the small diameter side end surface of the inner ring 4 in contact with the shoulder portion 100b of the drive shaft 100, is not tapered. It is larger than the area when it is formed. As a result, in the wheel bearing device 1, the frictional force between one side end of the inner ring 4 and the shoulder portion 100b of the drive shaft 100 increases, so that slippage occurs between the drive shaft 100 and the inner ring 4. hard. As a result, it is possible to prevent the generation of stick-slip noise for a long period of time without adding special parts.

以上、発明の実施の形態について、車輪用軸受装置１は、ハブ輪３の外周に一側ボール列５ａの内側転走面３ｄが直接形成されている第３世代構造の車輪用軸受装置１として構成されているがこれに限定するものではなく、ハブ輪３に一対の内輪が圧入固定された第２世代構造であっても良い。また、本発明は各実施形態に何等限定されるものではなく、あくまで例示であって、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、特許請求の範囲の記載によって示され、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。 As described above, according to the embodiment of the invention, the wheel bearing device 1 is a wheel bearing device 1 having a third generation structure in which the inner rolling surface 3d of the one-side ball row 5a is directly formed on the outer periphery of the hub wheel 3. Although it is configured, the structure is not limited to this, and a second generation structure in which a pair of inner rings are press-fitted and fixed to the hub wheel 3 may be used. Further, the present invention is not limited to each embodiment, but is merely an example, and it goes without saying that the present invention can be further implemented in various forms without departing from the gist of the present invention. The scope of the present invention is indicated by the description of the scope of claims, and further includes the equal meaning described in the scope of claims, and all modifications within the scope.

１ 車輪用軸受装置
２ 外輪
２ｅ 車体取り付けフランジ
２ｂ 他側開口部
３ ハブ輪
３ｂ 小径段部
３ｃ 車輪取り付けフランジ
４ 内輪
４ｂ 内輪嵌合孔
５ａ 一側ボール列
５ｂ 他側ボール列 1 Wheel bearing device 2 Outer ring 2e Body mounting flange 2b Other side opening 3 Hub wheel 3b Small diameter step 3c Wheel mounting flange 4 Inner ring 4b Inner ring fitting hole 5a One side ball row 5b Other side ball row

Claims (4)

内周に複列の外側転走面が一体に形成された外方部材と、
一端部に車輪を取り付けるための車輪取り付けフランジを一体に有し、外周に軸方向に延びる小径段部が形成され、内周にドライブシャフトがトルク伝達可能に係合される嵌合孔が形成されるハブ輪、およびこのハブ輪の小径段部に圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、
この内方部材と前記外方部材のそれぞれの転走面間に転動自在に収容された、複列の転動体と、を備えた車輪用軸受装置において、
前記小径段部と、前記小径段部が圧入される前記内輪の嵌合孔とがそれぞれ、前記ハブ輪の他端に向かうにつれて小径となるテーパ形状に形成される
車輪用軸受装置。 An outer member in which multiple rows of outer rolling surfaces are integrally formed on the inner circumference,
A wheel mounting flange for mounting a wheel is integrally provided at one end, a small diameter step portion extending in the axial direction is formed on the outer circumference, and a fitting hole is formed on the inner circumference in which a drive shaft is engaged so as to be able to transmit torque. An inner member composed of a hub wheel and at least one inner ring press-fitted into a small diameter step portion of the hub wheel, and a double-row inner rolling surface facing the outer rolling surface of the double-row is formed on the outer periphery thereof. When,
In a wheel bearing device including a double-row rolling element, which is rotatably accommodated between the rolling surfaces of the inner member and the outer member.
Wherein a cylindrical portion, wherein the said inner ring fitting hole cylindrical portion is press fitted respectively, the wheel bearing device is formed in a tapered shape whose diameter toward the other end of the wheel hub. 前記小径段部と前記内輪との嵌合において小径側端の締め代が最も大きくなるようにテーパ形状が形成される
請求項１に記載の車輪用軸受装置。 The wheel bearing device according to claim 1, wherein a tapered shape is formed so that the tightening allowance at the small diameter side end is maximized when the small diameter step portion and the inner ring are fitted. 前記小径段部と前記内輪との嵌合においてすべての嵌合部分に締め代が生じるようにテーパ形状が形成される
請求項１または請求項２に記載の車輪用軸受装置。 The wheel bearing device according to claim 1 or 2, wherein a tapered shape is formed so that a tightening allowance is generated in all the fitting portions when the small diameter step portion and the inner ring are fitted. 前記小径段部と前記内輪とのテーパ形状の少なくとも一部が、前記ハブ輪においてドライブシャフトが係合している部分と径方向視で重複する位置に形成される
請求項１から請求項３のいずれか一項に記載の車輪用軸受装置。 Claims 1 to 3 wherein at least a part of the tapered shape of the small diameter step portion and the inner ring is formed at a position where the hub ring overlaps with the portion where the drive shaft is engaged in the radial direction. The wheel bearing device according to any one of the following items.
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