JP6705363B2 - Rolling bearing unit for wheel support - Google Patents

Rolling bearing unit for wheel support Download PDF

Info

Publication number
JP6705363B2
JP6705363B2 JP2016211394A JP2016211394A JP6705363B2 JP 6705363 B2 JP6705363 B2 JP 6705363B2 JP 2016211394 A JP2016211394 A JP 2016211394A JP 2016211394 A JP2016211394 A JP 2016211394A JP 6705363 B2 JP6705363 B2 JP 6705363B2
Authority
JP
Japan
Prior art keywords
thin
female screw
axial
screw hole
thick
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2016211394A
Other languages
Japanese (ja)
Other versions
JP2018071644A (en
JP2018071644A5 (en
Inventor
山口　司
司 山口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2016211394A priority Critical patent/JP6705363B2/en
Priority to DE202017106535.9U priority patent/DE202017106535U1/en
Priority to CN201721413506.0U priority patent/CN207634514U/en
Publication of JP2018071644A publication Critical patent/JP2018071644A/en
Publication of JP2018071644A5 publication Critical patent/JP2018071644A5/ja
Application granted granted Critical
Publication of JP6705363B2 publication Critical patent/JP6705363B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B3/00—Disc wheels, i.e. wheels with load-supporting disc body
    • B60B3/14—Attaching disc body to hub ; Wheel adapters
    • B60B3/16—Attaching disc body to hub ; Wheel adapters by bolts or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0047—Hubs characterised by functional integration of other elements
    • B60B27/0052—Hubs characterised by functional integration of other elements the element being a brake disc
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0073—Hubs characterised by sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Description

本発明は、自動車の車輪を懸架装置に対して回転自在に支持する為の車輪支持用転がり軸受ユニットの改良に関する。 TECHNICAL FIELD The present invention relates to an improvement of a wheel supporting rolling bearing unit for rotatably supporting a vehicle wheel with respect to a suspension device.

自動車の車輪及びブレーキディスク等の制動用回転部材を懸架装置に対して回転自在に支持する為に、車輪支持用転がり軸受ユニットが広く使用されている。この様な車輪支持用転がり軸受ユニットは、使用される条件によって内輪回転型と外輪回転型の何れかのものが使用されている。 BACKGROUND OF THE INVENTION Wheel supporting rolling bearing units are widely used in order to rotatably support a vehicle wheel and a braking rotary member such as a brake disc with respect to a suspension device. As such a wheel-supporting rolling bearing unit, either an inner ring rotating type or an outer ring rotating type is used depending on the conditions under which it is used.

図４は、外輪回転型の車輪支持用転がり軸受ユニットとして、特許文献１に記載された従来構造の１例を示している。車輪支持用転がり軸受ユニット１は、静止側軌道輪である内径側軌道輪２と、回転側軌道輪である外径側軌道輪３と、それぞれが転動体である玉４、４とを備えている。 FIG. 4 shows an example of a conventional structure described in Patent Document 1 as an outer ring rotating type wheel supporting rolling bearing unit. The wheel supporting rolling bearing unit 1 includes an inner diameter side race ring 2 that is a stationary side race ring, an outer diameter side race ring 3 that is a rotating side race ring, and balls 4 and 4 that are rolling elements. There is.

内径側軌道輪２は、外周面に複列の内輪軌道５ａ、５ｂを有すると共に、内周面の軸方向内端部に、内径側軌道輪２を懸架装置に支持固定する為の内向フランジ状の静止側フランジ６を有している。外径側軌道輪３は、内周面に複列の外輪軌道７ａ、７ｂを有すると共に、外周面に車輪を支持固定する為の外向フランジ状の回転側フランジ８を有している。玉４、４は、内輪軌道５ａ、５ｂと外輪軌道７ａ、７ｂとの間に、両列毎にそれぞれ複数個ずつ、転動自在に設けられている。
尚、本明細書及び特許請求の範囲で、軸方向に関して「外」とは、車体への組み付け状態で車両の幅方向外側となる、図１、３、４の左側を言い、反対に、車体への組み付け状態で車両の幅方向中央側となる、図１、３、４の右側を、軸方向に関して「内」と言う。 The inner diameter side race ring 2 has double rows of inner ring raceways 5a, 5b on the outer peripheral surface, and an inward flange shape for supporting and fixing the inner diameter side race ring 2 to the suspension device at the axially inner end portion of the inner peripheral surface. Has a stationary side flange 6. The outer diameter side race ring 3 has double rows of outer ring raceways 7a and 7b on the inner peripheral surface, and also has an outward flange-shaped rotating flange 8 for supporting and fixing the wheel on the outer peripheral surface. A plurality of balls 4 and 4 are provided between the inner ring raceways 5a and 5b and the outer ring raceways 7a and 7b so that a plurality of balls can be rolled in each row.
In the present specification and claims, “outer” in the axial direction means the left side in FIGS. 1, 3, and 4, which is the outer side in the width direction of the vehicle when assembled to the vehicle body. The right side in FIGS. 1, 3, and 4, which is the center side in the width direction of the vehicle in the assembled state, is referred to as “inside” in the axial direction.

又、従来構造の場合、回転側フランジ８は、全体が円輪板状に構成されており、軸方向外側面は平坦面状であるのに対し、軸方向内側面は円周方向に関する凹凸形状となっている。この様な回転側フランジ８には、複数の薄肉部９と、これら各薄肉部９よりも軸方向厚さ寸法が大きく且つ軸方向内側に突出した複数の厚肉部１０とが、円周方向に関して交互に設けられている。又、円周方向に隣り合う薄肉部９同士は、これら薄肉部９の一部である薄肉連続部１１によって、厚肉部１０の径方向外側で円周方向に連続している。 Further, in the case of the conventional structure, the rotary side flange 8 is entirely formed in the shape of a circular plate, and the outer surface in the axial direction is flat, whereas the inner surface in the axial direction is uneven in the circumferential direction. Has become. In such a rotary side flange 8, a plurality of thin wall portions 9 and a plurality of thick wall portions 10 which are axially thicker than the respective thin wall portions 9 and project inward in the axial direction are formed in the circumferential direction. With respect to each other. Further, the thin-walled portions 9 that are adjacent to each other in the circumferential direction are circumferentially continuous outside the thick-walled portion 10 in the radial direction by the thin-walled continuous portion 11 that is a part of the thin-walled portions 9.

又、回転側フランジ８の円周方向等間隔となる複数箇所で、且つ、円周方向に関して厚肉部１０とそれぞれ整合する部分に、軸方向に貫通する状態で、雌ねじ孔１２が形成されている。そして、これら各雌ねじ孔１２に、図示しないボルトを螺合させる事で、回転側フランジ８に、車輪を構成するホイール及びディスクロータやドラムブレーキ等の制動用回転部材を支持固定する様にしている。 In addition, female screw holes 12 are formed in a plurality of positions at equal intervals in the circumferential direction of the rotary side flange 8 and at portions that respectively match the thick-walled portion 10 in the circumferential direction in a state of penetrating in the axial direction. There is. Then, a bolt (not shown) is screwed into each of the female screw holes 12 so that the rotation side flange 8 supports and fixes the wheel forming the wheel and the braking rotation member such as the disc rotor and the drum brake. ..

特開２０１２−５１３９３号公報JP2012-51393A 特開２０１５−１６７７７号公報JP, 2015-16777, A

ところで、上述した様な従来構造の車輪支持用転がり軸受ユニット１の場合、厚肉部１０に穿孔加工により形成する雌ねじ孔１２の形状精度及び寸法精度を確保する事が難しくなる。
この理由は、厚肉部１０の剛性が、厚肉部１０の軸方向位置によって異なる為である。具体的には、回転側フランジ８の径方向に関して雌ねじ孔１２の外側に存在する部分の厚さ寸法が、厚肉部１０の径方向外側に存在する薄肉連続部１１の分だけ軸方向外側部分で厚く、軸方向内側部分で薄くなっている為、厚肉部１０の剛性の大きさも、薄肉連続部１１と径方向に重畳した重畳部１３ａで高く、薄肉連続部１１と径方向に重畳していない非重畳部１３ｂで低くなる。この為、雌ねじ孔１２が途中で折れ曲がる（非重畳部１３ｂで径方向外側に折れ曲がる）といった問題や、雌ねじ孔１２の内径寸法が途中で変化する（重畳部１３ａでの内径寸法が非重畳部１３ｂでの内径寸法よりも大きくなる）といった問題を生じる可能性がある。 In the case of the wheel supporting rolling bearing unit 1 having the conventional structure as described above, it is difficult to secure the shape accuracy and dimensional accuracy of the female screw hole 12 formed in the thick wall portion 10 by drilling.
The reason is that the rigidity of the thick portion 10 differs depending on the axial position of the thick portion 10. Specifically, the thickness dimension of the portion existing outside the female screw hole 12 in the radial direction of the rotary side flange 8 is an axial outer portion corresponding to the thin continuous portion 11 existing outside the thick portion 10 in the radial direction. Since the thickness is thicker and the thickness is thinner in the axially inner portion, the rigidity of the thick portion 10 is also high in the overlapping portion 13a that overlaps the thin continuous portion 11 in the radial direction, and the rigidity of the thick continuous portion 11 in the radial direction overlaps. It becomes low in the non-overlapping part 13b. Therefore, the problem that the female screw hole 12 is bent in the middle (bending outward in the radial direction at the non-overlapping portion 13b) and the inner diameter dimension of the female screw hole 12 is changed in the middle (the inner diameter dimension in the overlapping portion 13a is the non-overlapping portion 13b). It becomes larger than the inner diameter of the above).

そして、雌ねじ孔１２が途中で折れ曲がるといった問題が生じた場合には、雌ねじ孔１２に螺合するボルトが折れ曲がる可能性がある。この為、車輪を構成するホイールや制動用回転部材の取り付け作業の作業性が低下する可能性がある。更に、ボルトの締め付け状態を締め付けトルクの大きさで管理する場合に、締め付けトルクの大きさに対応する軸力のばらつきが大きくなったり、ボルトに不要な応力が作用し易くなるといった問題を生じる可能性がある。 When a problem that the female screw hole 12 bends in the middle occurs, a bolt screwed into the female screw hole 12 may bend. Therefore, the workability of the work of mounting the wheels and the braking rotary member that constitute the wheel may be reduced. Further, when the tightening state of the bolt is managed by the magnitude of the tightening torque, there may be a problem that the variation of the axial force corresponding to the magnitude of the tightening torque becomes large and unnecessary stress is easily applied to the bolt. There is a nature.

又、雌ねじ孔の内径寸法が途中で変化するといった問題が生じた場合には、ボルトの外周面に形成された雄ねじと雌ねじ孔１２の内周面に形成された雌ねじとの螺合状態が、重畳部１３ａで緩く、非重畳部１３ｂで強くなる。この為、螺合部でフレッチング摩耗が発生し易くなるといった問題を生じる可能性がある。
本発明は、この様な事情に鑑みて、車輪や制動用回転部材を固定する為に利用する回転側フランジの雌ねじ孔の精度を十分に確保できる、車輪支持用転がり軸受ユニットの構造を実現すべく発明したものである。 In addition, when a problem occurs that the inner diameter of the female screw hole changes in the middle, the screwing state of the male screw formed on the outer peripheral surface of the bolt and the female screw formed on the inner peripheral surface of the female screw hole 12 is It becomes loose at the overlapping portion 13a and becomes strong at the non-overlapping portion 13b. Therefore, there is a possibility that fretting wear is likely to occur in the threaded portion.
In view of such circumstances, the present invention realizes a structure of a rolling bearing unit for wheel support, which can sufficiently secure the accuracy of the female screw hole of the rotary side flange used for fixing the wheel and the braking rotary member. It was invented accordingly.

本発明の車輪支持用転がり軸受ユニットは、静止側軌道輪と、回転側軌道輪と、複数個の転動体とを備える。
このうちの静止側軌道輪は、周面に１乃至複数の静止側軌道を有し、使用時に例えば懸架装置に支持固定されて回転しない。
又、前記回転側軌道輪は、周面に１乃至複数の回転側軌道を有すると共に、車輪及び制動用回転部材（例えばディスクロータやドラムブレーキ）を固定する為の外向フランジ状の回転側フランジを有し、使用時にこの車輪と共に回転する。
又、前記各転動体は、前記静止側軌道と前記回転側軌道との間に転動自在に設けられている。尚、この様な転動体としては、玉や円すいころ等を使用する事ができる。
又、本発明の車輪支持用転がり軸受ユニットの場合、前記回転側フランジは、全体が円周方向に連続する板状（例えば外周縁が円形状の円輪板状や、外周縁が５角形等の多角形となった多角板状）に構成されており、複数の薄肉部と、これら各薄肉部よりも軸方向厚さ寸法が大きく且つ軸方向内側に突出（膨出）した複数の厚肉部とが、円周方向に関して交互に設けられている。又、前記各薄肉部は、前記各厚肉部よりも径方向外方に延出しており、円周方向に隣り合う薄肉部同士は、前記各厚肉部の径方向外側で連続している。
そして、円周方向に関して前記各厚肉部と整合する部分には、これら各厚肉部を軸方向に貫通した取付孔をそれぞれ設けている。又、これら各取付孔を、軸方向内側の雌ねじ孔と、この雌ねじ孔よりも内径寸法が大きく且つ無ねじ状である軸方向外側の大径孔とから構成し、この大径孔の軸方向長さ寸法を、前記各薄肉部の軸方向厚さ寸法よりも大きくする。
尚、本発明を実施する場合に、前記大径孔としては、内径寸法が軸方向に亙り変化しない円筒孔とする事もできるし、内径寸法が軸方向に関して変化する（例えば軸方向外側に向かう程大きくなる）テーパ孔とする事もできる。大径孔を、内径寸法が軸方向外側に向かう程大きくなるテーパ孔とした場合には、車輪を固定する為のボルトを雌ねじ孔に螺合させ易くする事ができると共に、ハブ本体を加工する際の鍛造加工により大径孔を同時に形成する事ができる為、製造工程の簡略化を図る事もできる。
又、本発明を実施する場合に、前記回転フランジを構成する前記各厚肉部及び前記各薄肉部の数は、複数であれば良く、偶数又は奇数の別は特に問わない。 The wheel supporting rolling bearing unit of the present invention includes a stationary side bearing ring, a rotating side bearing ring, and a plurality of rolling elements.
Of these, the stationary raceway wheel has one or more stationary raceways on its peripheral surface, and is fixed to, for example, a suspension device and does not rotate during use.
Further, the rotating raceway wheel has one or more rotating side raceways on its peripheral surface, and has an outward flange-shaped rotating side flange for fixing the wheel and the braking rotary member (for example, a disc rotor or a drum brake). Have and rotate with this wheel when in use.
Further, each rolling element is provided between the stationary side raceway and the rotating side raceway so as to be rotatable. It should be noted that balls, tapered rollers and the like can be used as such rolling elements.
Further, in the case of the rolling bearing unit for wheel support according to the present invention, the rotary side flange is entirely in the form of a plate that is continuous in the circumferential direction (for example, an outer peripheral edge is a circular annular plate shape, or an outer peripheral edge is a pentagonal shape, etc.). Of a plurality of thin-walled portions, and a plurality of thick-walled portions having a larger axial thickness dimension than each of these thin-walled portions and projecting (bulging) inward in the axial direction. The parts and the parts are provided alternately in the circumferential direction. Further, the thin-walled portions extend outward in the radial direction from the thick-walled portions, and the thin-walled portions adjacent to each other in the circumferential direction are continuous on the radially outer side of the thick-walled portions. ..
Further, mounting holes are formed in the portions aligned with the thick portions in the circumferential direction so as to penetrate the thick portions in the axial direction. Each of these mounting holes is made up of an axially inner female screw hole and an axially outer large diameter hole having a larger inner diameter than the female screw hole and having no thread. The length dimension is made larger than the axial thickness dimension of each thin portion.
In the case of carrying out the present invention, the large-diameter hole may be a cylindrical hole whose inner diameter does not change in the axial direction, or the inner diameter changes in the axial direction (for example, toward the outer side in the axial direction). It can also be a tapered hole. If the large-diameter hole is a tapered hole whose inner diameter increases toward the outside in the axial direction, the bolts for fixing the wheel can be easily screwed into the female screw hole, and the hub body is processed. Since large-diameter holes can be simultaneously formed by the forging process at that time, the manufacturing process can be simplified.
Further, when carrying out the present invention, the number of the thick portions and the thin portions forming the rotary flange may be plural, and the number may be an even number or an odd number.

又、本発明を実施する場合には、例えば、前記回転側フランジのうち、円周方向に関して前記各薄肉部と整合する部分に、軸方向に貫通する状態で、透孔（作業用孔）を設ける事ができる。この場合に、これら各透孔は、前記回転側フランジに円周方向等間隔に設ける事ができる。
この様な透孔としては、軸方向から見た形状が円形状の円孔に限らず、例えば特許文献２に記載される様な軸方向から見た形状が扇台形状の通孔や、その他の多角形状の孔としても良い。 Further, when carrying out the present invention, for example, a through hole (working hole) is formed in a portion of the rotary side flange that is aligned with each of the thin portions in the circumferential direction in a state of penetrating in the axial direction. Can be provided. In this case, these through holes can be provided in the rotation-side flange at equal intervals in the circumferential direction.
Such a through hole is not limited to a circular hole having a circular shape when viewed from the axial direction. For example, a through hole having a fan-shaped shape when viewed from the axial direction as described in Patent Document 2 or the like. It may be a polygonal hole.

本発明の車輪支持用転がり軸受ユニットによれば、車輪や制動用回転部材を固定する為に利用する回転側フランジの雌ねじ孔の精度を十分に確保できる。
即ち、本発明の場合には、回転側フランジを構成する厚肉部を軸方向に貫通する状態で設けた取付孔を、軸方向内側の雌ねじ孔と軸方向外側の大径孔とから構成し、更にこの大径孔の軸方向長さ寸法を、回転側フランジを構成する薄肉部（薄肉連続部）の軸方向厚さ寸法よりも大きくしている。この為、回転側フランジの径方向に関して雌ねじ孔の外側に存在する部分の厚さ寸法を一定にできる。この為、厚肉部のうちで、雌ねじ孔を形成する部分（範囲）の剛性を、軸方向に関して一定にできる。従って、雌ねじ孔が途中で折れ曲がったり、雌ねじ孔の内径寸法が途中で変化したりする事を防止できる。この結果、本発明によれば、雌ねじ孔の精度（形状精度及び寸法精度）を十分に確保できる。 According to the wheel supporting rolling bearing unit of the present invention, it is possible to sufficiently secure the accuracy of the female screw hole of the rotary side flange used for fixing the wheel and the braking rotary member.
That is, in the case of the present invention, the mounting hole provided in a state of penetrating in the axial direction the thick-walled portion that constitutes the rotary side flange is composed of an axially inner female screw hole and an axially outer large diameter hole. Further, the axial length dimension of the large diameter hole is made larger than the axial thickness dimension of the thin wall portion (thin wall continuous portion) forming the rotary side flange. Therefore, the thickness dimension of the portion existing outside the female screw hole in the radial direction of the rotary side flange can be made constant. Therefore, the rigidity of the portion (range) forming the female screw hole in the thick portion can be made constant in the axial direction. Therefore, it is possible to prevent the female screw hole from being bent halfway and the internal diameter of the female screw hole from being changed halfway. As a result, according to the present invention, the accuracy (shape accuracy and dimensional accuracy) of the female screw hole can be sufficiently ensured.

本発明の実施の形態の第１例を示す、車輪支持用転がり軸受ユニットの断面図。Sectional drawing of the rolling bearing unit for wheel support which shows the 1st example of embodiment of this invention. 同じくハブ本体を取り出して、軸方向内側から見た図。Similarly, a view of the hub body taken out and seen from the inside in the axial direction. 本発明の実施の形態の第２例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. 従来構造の車輪支持用転がり軸受ユニットの１例を示す断面図。Sectional drawing which shows an example of the rolling bearing unit for wheel support of a conventional structure.

［実施の形態の第１例］
本発明の実施の形態の第１例に就いて、図１〜２を参照しつつ説明する。本例の車輪支持用転がり軸受ユニット１ａは、内輪回転型で、懸架装置を構成するナックルに対し、従動輪である車輪を構成するホイール及び制動用回転部材（ディスクロータ）を回転自在に支持する為のものであり、外輪１４の内径側にハブ１５を、複数個の玉１６、１６を介して回転自在に支持している。本例の場合、外輪１４が、特許請求の範囲に記載した静止側軌道輪に相当し、ハブ１５が、特許請求の範囲に記載した回転側軌道輪に相当し、玉１６が、特許請求の範囲に記載した転動体に相当する。 [First Example of Embodiment]
A first example of the embodiment of the present invention will be described with reference to FIGS. The wheel supporting rolling bearing unit 1a of the present example is an inner ring rotating type and rotatably supports a wheel forming a wheel as a driven wheel and a rotating member for braking (a disc rotor) with respect to a knuckle forming a suspension device. The hub 15 is rotatably supported on the inner diameter side of the outer ring 14 via a plurality of balls 16, 16. In the case of this example, the outer ring 14 corresponds to the stationary side race ring described in the claims, the hub 15 corresponds to the rotating side race ring described in the claims, and the ball 16 corresponds to the claims. It corresponds to the rolling element described in the range.

外輪１４は、例えば中炭素鋼等の鉄系合金製で、全体が略円筒状に構成されており、内周面に複列の外輪軌道１７ａ、１７ｂを、外周面に静止側フランジ１８を、それぞれ有している。この様な外輪１４は、静止側フランジ１８の円周方向複数箇所に形成したねじ孔１８ａに螺合した複数本のボルトにより、図示しないナックルに固定される。 The outer ring 14 is made of an iron-based alloy such as medium carbon steel, and has a substantially cylindrical shape as a whole. The outer ring raceways 17a and 17b are arranged in multiple rows on the inner peripheral surface, and the stationary side flange 18 is formed on the outer peripheral surface. I have each. Such an outer ring 14 is fixed to a knuckle (not shown) by a plurality of bolts screwed into screw holes 18a formed at a plurality of positions in the circumferential direction of the stationary side flange 18.

ハブ１５は、ハブ本体１９と内輪２０とを結合する事により構成されており、外周面に複列の内輪軌道２１ａ、２１ｂと外向フランジ状の回転側フランジ２２とを有している。そして、使用時に、ハブ１５は、回転側フランジ２２に結合固定した、図示しないホイール及び制動用回転部材と共に回転する。 The hub 15 is configured by connecting the hub body 19 and the inner ring 20 and has double rows of inner ring raceways 21a and 21b and an outward flange-shaped rotating side flange 22 on the outer peripheral surface. Then, during use, the hub 15 rotates together with the wheel and the braking rotary member (not shown) fixedly coupled to the rotary side flange 22.

ハブ本体１９は、例えば中炭素鋼等の素材に鍛造加工を施す事により造られている。又、このハブ本体１９の外周面のうち、軸方向外端寄り部分に回転側フランジ２２を、軸方向中間部に外側列の内輪軌道２１ａを、軸方向内端寄り部分に小径段部２３を、それぞれ直接形成している。又、ハブ本体１９の径方向中央部には、軸方向外端面にのみ開口した凹部４８が設けられている。 The hub body 19 is made by forging a material such as medium carbon steel. Further, on the outer peripheral surface of the hub body 19, the rotary side flange 22 is provided at the axially outer end portion, the outer row inner ring raceway 21a is provided at the axially intermediate portion, and the small diameter step portion 23 is provided at the axial inner end portion. , Each directly formed. Further, a concave portion 48 that is opened only on the axially outer end surface is provided at the radial center of the hub body 19.

内輪２０は、例えばＳＵＪ２等の高炭素クロム軸受鋼製で、全体が円環状に構成されており、その外周面に、内側列の内輪軌道２１ｂを形成している。この様な内輪２０は、ハブ本体１９の小径段部２３に締り嵌めにより外嵌固定されている。そして、内輪２０は、このハブ本体１９の軸方向内端部に形成したかしめ部２４により、軸方向内端面が抑え付けられている。尚、ハブ本体１９の軸方向内端部にかしめ部２４を形成する構造に代えて、ハブ本体の軸方向内端部にナットを螺着する構造を採用する事もできる。 The inner ring 20 is made of high carbon chrome bearing steel such as SUJ2, and is formed in an annular shape as a whole, and the inner ring raceway 21b of the inner row is formed on the outer peripheral surface thereof. Such an inner ring 20 is externally fitted and fixed to the small-diameter step portion 23 of the hub body 19 by interference fitting. The inner ring 20 has its axially inner end surface suppressed by a caulking portion 24 formed at the axially inner end of the hub body 19. It should be noted that instead of the structure in which the caulking portion 24 is formed at the axially inner end portion of the hub body 19, a structure in which a nut is screwed to the axially inner end portion of the hub body may be adopted.

玉１６、１６は、例えば軸受鋼製やセラミック製で、複列の外輪軌道１７ａ、１７ｂと複列の内輪軌道２１ａ、２１ｂとの間に、保持器２５ａ、２５ｂに保持された状態で、各列毎に複数個ずつ、転動自在に設けられている。又、玉１６、１６には、予圧と共に背面組み合わせ型の接触角が付与されている。これにより、ハブ１５を外輪１４の内径側に、がたつきなく、且つ、ラジアル荷重及びアキシアル荷重を支承しつつ回転可能に支持している。尚、図示の例では、転動体として玉１６、１６を使用した場合を示したが、重量が嵩む自動車用の車輪支持用転がり軸受ユニットの場合には、玉に代えて円すいころを使用する事もできる。 The balls 16, 16 are made of, for example, bearing steel or ceramic, and are held by the cages 25a, 25b between the double row outer ring raceways 17a, 17b and the double row inner ring raceways 21a, 21b, respectively. A plurality of rolls are provided for each row. Further, the balls 16 and 16 are provided with a back combination type contact angle together with a preload. As a result, the hub 15 is rotatably supported on the inner diameter side of the outer ring 14 without rattling and while supporting the radial load and the axial load. In the illustrated example, balls 16 are used as rolling elements, but in the case of a rolling bearing unit for wheel support for automobiles, which has a large weight, use tapered rollers instead of balls. You can also

外輪１４の内周面とハブ１５の外周面との間に存在する、内部空間（転動体設置空間）２６の軸方向両端開口を、シールリング２７及びカバー２８により塞いでいる。このうちのシールリング２７は、金属板製の芯金２９と弾性材製のシール材３０とを備えている。そして、このうちの芯金２９を外輪１４の軸方向外端部内周面に内嵌固定した状態で、シール材３０に設けられた複数本（図示の例では４本）のシールリップ３１ａ〜３１ｄの先端縁をハブ１５の表面に、全周に亙り摺接（又は近接対向）させている。これにより、内部空間２６の軸方向外端開口部を塞いでいる。 A seal ring 27 and a cover 28 close the openings at both axial ends of the internal space (rolling element installation space) 26 existing between the inner peripheral surface of the outer ring 14 and the outer peripheral surface of the hub 15. The seal ring 27 includes a core metal 29 made of a metal plate and a sealing material 30 made of an elastic material. Then, a plurality of (four in the illustrated example) seal lips 31a to 31d provided on the seal material 30 in a state where the core metal 29 among them is fitted and fixed to the inner peripheral surface of the outer end portion of the outer ring 14 in the axial direction. The leading edge of the above is slidably contacted (or closely opposed) to the surface of the hub 15 over the entire circumference. As a result, the axially outer end opening of the internal space 26 is closed.

これに対し、カバー２８は、外輪１４の軸方向内端開口部を塞ぐ事により、内部空間２６の軸方向内端開口を塞ぐものであり、非磁性材性で、全体が有底円筒状に構成されている。この様なカバー２８は、略円筒状の支持筒部３２と、この支持筒部３２の軸方向内端部から径方向内方に折れ曲がった底板部３３とを備えている。そして、このうちの支持筒部３２を、外輪１４の軸方向内端部に内嵌固定する事で、径方向内側が軸方向に貫通していないハブ本体１９の軸方向内側面と共に、内部空間２６の軸方向内端開口を塞いでいる。又、支持筒部３２の軸方向内端部外周面を覆ったシール材３４により、支持筒部３２の軸方向内端部外周面と外輪１４の軸方向内端部内周面との間をシールしている。 On the other hand, the cover 28 closes the axial inner end opening of the outer ring 14 to close the axial inner end opening of the inner space 26, and is made of a non-magnetic material and has a bottomed cylindrical shape. It is configured. Such a cover 28 is provided with a substantially cylindrical support tubular portion 32 and a bottom plate portion 33 bent inward in the radial direction from the axially inner end portion of the support tubular portion 32. Then, by internally fitting and fixing the support tubular portion 32 among these to the axially inner end portion of the outer ring 14, the inner space along with the axially inner side surface of the hub body 19 whose radially inner side does not penetrate axially is formed. The opening 26 in the axial direction is closed. In addition, the seal member 34 covering the outer peripheral surface of the inner end portion of the support tubular portion 32 in the axial direction seals between the outer peripheral surface of the inner peripheral portion of the support tubular portion 32 in the axial direction and the inner peripheral surface of the inner end portion of the outer ring 14. is doing.

又、ハブ１５に結合固定した車輪の回転速度を測定可能とすべく、エンコーダ３５を、磁性金属製の支持環３６を介して内輪２０の肩部に支持固定している。エンコーダ３５は、ゴム磁石、プラスチック磁石等の永久磁石製で、全体が円輪状に構成されており、軸方向に着磁されている。着磁方向は、円周方向に関して、交互に、且つ、等間隔で変化させている。従って、被検出面である、エンコーダ３５の軸方向内側面には、Ｓ極とＮ極とが、円周方向に関して、交互に、且つ、等間隔で配置されている。そして、この様なエンコーダ３５の被検出面には、カバー２８を構成する底板部３３の外径側部分を介して、図示しないセンサの検出部を対向させる。これにより、ハブ１５と共に回転する車輪の回転速度を測定する。そして、測定した車輪の回転速度を表す信号を、アンチロックブレーキシステム（ＡＢＳ）やトラクションコントロールシステム（ＴＣＳ）等、車両の走行安定化装置の制御に利用する。 The encoder 35 is supported and fixed to the shoulder portion of the inner ring 20 via a support ring 36 made of magnetic metal so that the rotational speed of the wheel coupled and fixed to the hub 15 can be measured. The encoder 35 is made of a permanent magnet such as a rubber magnet or a plastic magnet, and has a circular ring shape as a whole, and is magnetized in the axial direction. The magnetizing directions are changed alternately and at equal intervals in the circumferential direction. Therefore, the S poles and the N poles are alternately arranged at equal intervals in the circumferential direction on the inner surface of the encoder 35 in the axial direction, which is the detected surface. Then, a detection portion of a sensor (not shown) is made to face the detection surface of such an encoder 35 via the outer diameter side portion of the bottom plate portion 33 that constitutes the cover 28. With this, the rotational speed of the wheel that rotates together with the hub 15 is measured. Then, the signal representing the measured rotation speed of the wheel is used for controlling a vehicle running stabilizing device such as an antilock brake system (ABS) or a traction control system (TCS).

又、ハブ本体１９の軸方向外端寄り部分に設けられた回転側フランジ２２は、全体が円輪板状に構成されており、制動用回転部材の取付面となる軸方向外側面は、ハブ本体１９の中心軸に対し直交する仮想平面上に存在する平坦面となっている。又、本例の回転側フランジ２２は、径方向内端部に、軸方向厚さ寸法が全周に亙り変化しない根元部３７が設けられているのに対し、径方向中間部に、軸方向厚さ寸法が円周方向に関して変化する肉厚変化部３８が設けられている。この為、回転側フランジ２２の軸方向内側面は、径方向内端部の根元部３７では、ハブ１５の中心軸に対し直交する仮想平面上に存在する平坦面となっているのに対し、径方向中間部に位置する肉厚変化部３８では、円周方向に関する凹凸形状となっている。 Further, the rotary side flange 22 provided on the portion of the hub body 19 near the axially outer end is formed in the shape of a circular plate, and the axially outer side surface serving as the mounting surface of the braking rotary member is the hub. It is a flat surface existing on a virtual plane orthogonal to the central axis of the main body 19. In addition, in the rotary side flange 22 of this example, a root portion 37 whose axial thickness dimension does not change over the entire circumference is provided at an inner end portion in the radial direction, while a radial direction intermediate portion is provided with an axial direction. A wall thickness changing portion 38 whose thickness dimension changes in the circumferential direction is provided. Therefore, the axially inner side surface of the rotary side flange 22 is a flat surface existing on an imaginary plane orthogonal to the central axis of the hub 15 at the root portion 37 at the radially inner end, whereas The wall thickness changing portion 38 located at the middle portion in the radial direction has an uneven shape in the circumferential direction.

又、回転側フランジ２２の径方向中間部（肉厚変化部３８）には、複数（図示の例では５つ）の薄肉部３９、３９と、これら各薄肉部３９、３９よりも軸方向厚さ寸法が大きく且つ軸方向内側に突出（膨出）すると共に放射方向に伸長した複数（図示の例では５つ）の厚肉部４０、４０とが、円周方向に関して交互に設けられている。図示の例の場合、薄肉部３９、３９（厚肉部４０、４０）の円周方向に関する位相は７２度ずつ等間隔にずれている。又、薄肉部３９、３９は、厚肉部４０、４０よりも径方向外方に僅かに延出する状態で設けられており、円周方向に隣り合う薄肉部３９、３９同士は、これら薄肉部３９、３９の一部である薄肉連続部４１によって、厚肉部４０、４０の径方向外側で円周方向に連続している。従って、回転側フランジ２２の径方向外端部には、薄肉部３９（及び薄肉連続部４１）が全周に亙り連続する状態で設けられている。 Further, a plurality of (five in the illustrated example) thin-walled portions 39, 39 are formed in the radial middle portion (thickness changing portion 38) of the rotary side flange 22, and an axial thickness greater than these thin-walled portions 39, 39. A plurality of (five in the illustrated example) thick portions 40, 40 that are large in size and project (bulge) inward in the axial direction and extend in the radial direction are provided alternately in the circumferential direction. .. In the illustrated example, the phases of the thin portions 39, 39 (thick portions 40, 40) in the circumferential direction are shifted by 72 degrees at equal intervals. Further, the thin-walled portions 39, 39 are provided so as to extend slightly outward in the radial direction from the thick-walled portions 40, 40, and the thin-walled portions 39, 39 adjacent to each other in the circumferential direction are provided with these thin-walled portions 39, 39. A thin continuous portion 41, which is a part of the portions 39, 39, is circumferentially continuous outside the thick portions 40, 40 in the radial direction. Accordingly, the thin portion 39 (and the thin continuous portion 41) is provided at the radially outer end of the rotary side flange 22 in a continuous state over the entire circumference.

又、厚肉部４０の軸方向厚さ寸法Ｘは、根元部３７の軸方向厚さ寸法とほぼ同じであり、薄肉部３９の軸方向厚さ寸法Ｙのおよそ２〜６倍程度（図示の例では４倍）に設定されている。尚、薄肉部３９の軸方向厚さ寸法Ｙは、回転側フランジ２２の円周方向に関して厚肉部４０に隣接する部分と、径方向に関して厚肉部４０の外側に位置する部分（薄肉連続部４１）とで、互いに同じである。 Further, the axial thickness dimension X of the thick portion 40 is almost the same as the axial thickness dimension of the root portion 37, and is about 2 to 6 times the axial thickness dimension Y of the thin portion 39 (shown in the figure). (4 times in the example). In addition, the axial thickness dimension Y of the thin portion 39 is defined by the portion adjacent to the thick portion 40 in the circumferential direction of the rotary side flange 22 and the portion located outside the thick portion 40 in the radial direction (thin continuous portion). 41) and are the same as each other.

回転側フランジ２２の円周方向等間隔複数箇所（図示の例では５箇所）で、且つ、円周方向に関して厚肉部４０、４０とそれぞれ整合する部分のうち、これら厚肉部４０、４０の円周方向中央に位置する部分に、軸方向に貫通する状態で、取付孔４２、４２を設けている。本例の場合には、取付孔４２を、軸方向外側の大径孔４３と、軸方向内側の雌ねじ孔４４との２種類の孔から構成している。別な言い方をすれば、厚肉部４０の軸方向外側面から軸方向中間部に亙る範囲に大径孔４３を形成し、厚肉部４０の軸方向内側面から軸方向中間部に亙る範囲に雌ねじ孔４４を形成している。又、軸方向外側の大径孔４３と軸方向内側の雌ねじ孔４４とは同軸上に配置されている。 Of the plurality of circumferentially equally spaced portions of the rotary side flange 22 (five in the illustrated example) and of the portions that respectively match the thick portions 40, 40 in the circumferential direction, these thick portions 40, 40 Mounting holes 42, 42 are provided in a portion located at the center in the circumferential direction in a state of penetrating in the axial direction. In the case of this example, the mounting hole 42 is composed of two types of holes, a large diameter hole 43 on the outside in the axial direction and a female screw hole 44 on the inside in the axial direction. In other words, the large-diameter hole 43 is formed in a range extending from the axially outer side surface of the thick portion 40 to the axial intermediate portion, and the large-diameter hole 43 is formed from the axial inner surface of the thick portion 40 to the axial intermediate portion. A female screw hole 44 is formed in the. Further, the large diameter hole 43 on the outer side in the axial direction and the female screw hole 44 on the inner side in the axial direction are arranged coaxially.

大径孔４３は、内周面が単一円筒面である円筒孔で、無ねじ状に構成されているのに対し、雌ねじ孔４４は、内周面に雌ねじが形成されている。又、大径孔４３の内径寸法は、雌ねじ孔４４の内径寸法（雌ねじの歯底円の直径寸法）よりも大きく設定されており、軸方向に亙り変化しない。特に本例の場合には、この様な大径孔４３の軸方向長さ寸法Ａを、薄肉部３９（薄肉連続部４１）の軸方向厚さ寸法Ｙよりも大きく設定している（Ａ＞Ｙ）。これにより、大径孔４３と雌ねじ孔４４との境界位置を、厚肉部４０のうちで薄肉連続部４１と径方向に重畳した重畳部４５ａではなく、厚肉部４０のうちで薄肉連続部４１と径方向に重畳していない非重畳部４５ｂに位置させている。この為、雌ねじ孔４４は、厚肉部４０のうちの非重畳部４５ｂにのみ形成されており、重畳部４５ａには形成されていない。 The large-diameter hole 43 is a cylindrical hole whose inner peripheral surface is a single cylindrical surface, and has a non-threaded shape, whereas the female screw hole 44 has an internal thread formed on the inner peripheral surface. Further, the inner diameter of the large diameter hole 43 is set larger than the inner diameter of the female screw hole 44 (diameter of the root circle of the female screw) and does not change in the axial direction. Particularly in the case of this example, the axial length dimension A of the large-diameter hole 43 is set larger than the axial thickness dimension Y of the thin portion 39 (thin continuous portion 41) (A> Y). As a result, the boundary position between the large-diameter hole 43 and the female screw hole 44 is not the overlapping portion 45a of the thick-walled portion 40 that overlaps the thin-walled continuous portion 41 in the radial direction, but the thin-walled continuous portion of the thick-walled portion 40. 41 is located in the non-overlapping portion 45b that does not overlap with 41 in the radial direction. Therefore, the female screw hole 44 is formed only in the non-overlapping portion 45b of the thick portion 40, and is not formed in the overlapping portion 45a.

又、非重畳部４５ｂの外周側面（外径面）は、取付孔４２（雌ねじ孔４４）と同心の部分円筒形状であり、非重畳部４５ｂの外周側面と雌ねじ孔４４の内周面との間の肉厚は、回転側フランジ２２の径方向に関して雌ねじ孔４４の外側に位置する部分で、円周方向及び軸方向に関してほぼ一定である。これに対し、回転側フランジ２２の径方向に関して雌ねじ孔４４の内側に位置する部分のうち、凹部４８の内周面と雌ねじ孔４４の内周面との間部分の肉厚は、円周方向に関して変化するが、軸方向に関してほぼ一定である。但し、凹部４８の内周面と雌ねじ孔４４の内周面との間の肉厚は、非重畳部４５ｂの外周側面と雌ねじ孔４４の内周面との間の肉厚よりも十分に大きいので、回転側フランジ２２の径方向に関して雌ねじ孔４４の内側に位置する部分の肉厚変化は、雌ねじ孔４４を形成する部分（範囲）の剛性変化に殆ど影響を与える事はない。 Further, the outer peripheral side surface (outer diameter surface) of the non-overlapping portion 45b has a partial cylindrical shape concentric with the mounting hole 42 (female screw hole 44), and the outer peripheral side surface of the non-overlapping portion 45b and the inner peripheral surface of the female screw hole 44 are formed. The wall thickness between them is a portion located outside the female screw hole 44 in the radial direction of the rotary side flange 22, and is substantially constant in the circumferential direction and the axial direction. On the other hand, the wall thickness of the portion between the inner peripheral surface of the recess 48 and the inner peripheral surface of the female screw hole 44 in the portion located inside the female screw hole 44 in the radial direction of the rotary side flange 22 is the circumferential direction. , But it is almost constant in the axial direction. However, the wall thickness between the inner peripheral surface of the concave portion 48 and the inner peripheral surface of the female screw hole 44 is sufficiently larger than the wall thickness between the outer peripheral side surface of the non-overlapping portion 45b and the inner peripheral surface of the female screw hole 44. Therefore, the change in the wall thickness of the portion located inside the female screw hole 44 in the radial direction of the rotary side flange 22 hardly affects the change in the rigidity of the portion (range) forming the female screw hole 44.

上述した様な取付孔４２を形成するには、例えば、先ず、回転側フランジ２２のうち、円周方向に関して厚肉部４０と整合する部分に、大径孔４３を、軸方向外側から軸方向内側に向けて、その奥端部が非重畳部４５ｂにまで達する様に形成する。次いで、この大径孔４３と同軸上に軸方向に貫通する状態で下孔を形成する。その後、下孔にタップで雌ねじを形成する事により、雌ねじ孔４４を形成する。尚、タッピングドリルを用いて下孔の形成と雌ねじ孔４４の形成を同時に行う事もできる。本例の場合には、この様にして、軸方向外側に大径孔４３が設けられると共に、軸方向内側に雌ねじ孔４４が設けられた、本例の取付孔４２を形成する。 In order to form the mounting hole 42 as described above, for example, first, a large diameter hole 43 is formed in the rotation side flange 22 in a portion aligned with the thick portion 40 in the circumferential direction from the axial outside to the axial direction. The inner end is formed so as to reach the non-overlapping portion 45b. Next, a pilot hole is formed coaxially with the large diameter hole 43 so as to penetrate therethrough in the axial direction. Then, a female screw hole 44 is formed by tapping a female screw in the pilot hole. It is also possible to use a tapping drill to simultaneously form the pilot hole and the female screw hole 44. In the case of this example, in this way, the mounting hole 42 of this example is formed in which the large diameter hole 43 is provided on the outside in the axial direction and the female screw hole 44 is provided on the inside in the axial direction.

そして、本例の場合にも、ホイール及び制動用回転部材にそれぞれ形成された通孔内に、ボルトを挿通した後、ボルトの先端部に形成された雄ねじを、取付孔４２を構成する雌ねじ孔４４に螺合させる。これにより、回転側フランジ２２の軸方向外側面に、制動用回転部材及びホイールを固定する。 Also in the case of this example, after the bolt is inserted into the through holes formed in the wheel and the braking rotary member respectively, the male screw formed at the tip of the bolt is inserted into the female screw hole forming the mounting hole 42. It is screwed to 44. As a result, the braking rotation member and the wheel are fixed to the axially outer surface of the rotation side flange 22.

又、車輪支持用転がり軸受ユニット１ａの軽量化、又は、図示しない足回り部品の取り付け若しくは取り外しに使用する工具を挿入する為に、回転側フランジ２２の円周方向等間隔複数箇所（５箇所）で、且つ、円周方向に関して薄肉部３９、３９とそれぞれ整合する部分に、軸方向に貫通する状態で、円形状の透孔４６、４６を設けている。これら各透孔４６、４６は、厚肉部４０、４０に設けられた取付孔４２、４２（大径孔４３）よりも大きな内径寸法を有している。又、回転側フランジ２２のうち、円周方向に関して薄肉部３９、３９と整合する部分で、且つ、円周方向に関して透孔４６、４６から外れた部分には、回転側フランジ２２から制動用回転部材を取り外すのに利用する押しボルトを螺合させる為のねじ孔４７、４７を設けている。 Further, in order to reduce the weight of the wheel-supporting rolling bearing unit 1a, or to insert a tool used for attaching or removing an underbody component (not shown), a plurality of locations (5 locations) at equal intervals in the circumferential direction of the rotary side flange 22 are provided. In addition, circular through holes 46, 46 are provided in the portions aligned with the thin portions 39, 39 in the circumferential direction so as to penetrate in the axial direction. Each of these through holes 46, 46 has an inner diameter larger than the mounting holes 42, 42 (large diameter holes 43) provided in the thick portions 40, 40. Further, in the portion of the rotary side flange 22 which is aligned with the thin portions 39, 39 in the circumferential direction, and which is out of the through holes 46, 46 in the circumferential direction, the rotary side flange 22 is rotated for braking. Screw holes 47, 47 for screwing a push bolt used for removing the member are provided.

以上の様な構成を有する本例の場合には、車輪を構成するホイールや制動用回転部材を固定する為に利用する回転側フランジ２２の雌ねじ孔４４の精度を十分に確保できる。
即ち、本例の場合には、厚肉部４０を軸方向に貫通する状態で設けた取付孔４２を、軸方向外側の大径孔４３と軸方向内側の雌ねじ孔４４とから構成し、更にこの大径孔４３の軸方向長さ寸法Ａを、薄肉部３９（薄肉連続部４１）の軸方向厚さ寸法Ｙよりも大きくしている。この為、本例の場合には、回転側フランジ２２の径方向に関して雌ねじ孔４４の外側に存在する部分の厚さ寸法を一定にできる。この為、厚肉部４０のうちで、雌ねじ孔４４を形成する部分（範囲）の剛性を、軸方向に関して一定にできる。従って、雌ねじ孔４４を穿孔加工により形成する際に、この雌ねじ孔４４が途中で折れ曲がったり、雌ねじ孔４４の内径寸法が途中で変化したりする事を防止できる。この結果、本例の場合には、雌ねじ孔４４の精度（形状精度及び寸法精度）を十分に確保できる。これにより、雌ねじ孔の精度が不十分である事に起因して生じる、ボルトの折れ曲がりや螺合部でのフレッチング摩耗等の前述した各種の問題の発生を有効に防止できる。 In the case of the present example having the above-described configuration, it is possible to sufficiently secure the accuracy of the female screw hole 44 of the rotary side flange 22 used for fixing the wheel and the braking rotary member that configure the wheel.
That is, in the case of this example, the mounting hole 42 provided in the state of penetrating the thick portion 40 in the axial direction is constituted by the large diameter hole 43 on the outer side in the axial direction and the female screw hole 44 on the inner side in the axial direction. The axial length dimension A of the large diameter hole 43 is made larger than the axial thickness dimension Y of the thin portion 39 (thin continuous portion 41). Therefore, in the case of this example, the thickness dimension of the portion existing outside the female screw hole 44 in the radial direction of the rotary side flange 22 can be made constant. Therefore, in the thick portion 40, the rigidity of the portion (range) where the female screw hole 44 is formed can be made constant in the axial direction. Therefore, when the female screw hole 44 is formed by punching, it is possible to prevent the female screw hole 44 from being bent halfway and the inner diameter of the female screw hole 44 from being changed halfway. As a result, in the case of this example, the accuracy (shape accuracy and dimensional accuracy) of the female screw hole 44 can be sufficiently ensured. As a result, it is possible to effectively prevent the above-described various problems such as bending of the bolt and fretting wear at the threaded portion, which are caused by insufficient precision of the female screw hole.

［実施の形態の第２例］
本発明の実施の形態の第２例に就いて、図３を参照しつつ説明する。本例の車輪支持用転がり軸受ユニット１ｂは、前述した従来構造の場合と同様に、外輪回転型で、静止側軌道輪である内径側軌道輪２ａと、回転側軌道輪である外径側軌道輪３ａと、それぞれが転動体である玉４ａ、４ａとを備えている。 [Second Example of Embodiment]
A second example of the embodiment of the present invention will be described with reference to FIG. The wheel supporting rolling bearing unit 1b of the present example is an outer ring rotating type and has an inner diameter side race ring 2a which is a stationary side race ring and an outer diameter side raceway which is a rotating side race ring, as in the case of the conventional structure described above. The wheel 3a is provided with balls 4a and 4a, which are rolling elements.

内径側軌道輪２ａは、外周面に複列の内輪軌道５ｃ、５ｄを有すると共に、内周面の軸方向内端部に、内径側軌道輪２ａを懸架装置に支持固定する為の図示しない静止側フランジを有している。この様な内径側軌道輪２ａは、主部４９と、主部４９の軸方向外端部に外嵌固定した内輪素子５０とを、主部４９の軸方向外端部に形成したかしめ部５１により結合する事により構成されている。これら主部４９及び内輪素子５０は、それぞれ焼き入れ硬化可能な鉄系合金製であり、このうちの内輪素子５０の外周面に、外側列の内輪軌道５ｃを形成しており、主部４９の軸方向中間部外周面に内側列の内輪軌道５ｄを形成している。又、これら両内輪軌道５ｃ、５ｄのうち、内側列の内輪軌道５ｄの外径寸法は、外側列の内輪軌道５ｃの外径寸法よりも大きくなっている。 The inner diameter side race ring 2a has double rows of inner ring raceways 5c and 5d on the outer peripheral surface, and a stationary member (not shown) for supporting and fixing the inner diameter side race ring 2a to the suspension device at the axially inner end portion of the inner peripheral surface. It has side flanges. In such an inner diameter side race ring 2a, the main portion 49 and the inner ring element 50 fitted and fixed to the outer end portion of the main portion 49 in the axial direction are formed at the outer end portion of the main portion 49 in the axial direction. It is composed by combining with. The main portion 49 and the inner ring element 50 are each made of a quench-hardenable iron-based alloy, and the inner ring raceway 5c of the outer row is formed on the outer peripheral surface of the inner ring element 50, and the main portion 49 The inner ring raceway 5d of the inner row is formed on the outer peripheral surface of the intermediate portion in the axial direction. Of these inner ring raceways 5c and 5d, the outer diameter dimension of the inner ring raceway 5d in the inner row is larger than the outer diameter dimension of the inner ring raceway 5c in the outer row.

外径側軌道輪３ａは、内周面に複列の外輪軌道７ｃ、７ｄを有すると共に、外周面に車輪を支持固定する為の外向フランジ状の回転側フランジ８ａを有している。この様な外径側軌道輪３ａは、中炭素鋼等の焼き入れ硬化可能な鉄系合金製であり、内径側軌道輪２ａの周囲に、この内径側軌道輪２ａと同心に配置されている。外径側軌道輪３ａの内周面に形成された外輪軌道７ｃ、７ｄは、内側列の外輪軌道７ｄの内径寸法が、外側列の外輪軌道７ｃの内径寸法よりも大きくなっている。 The outer diameter side race ring 3a has double rows of outer ring raceways 7c and 7d on the inner peripheral surface, and also has an outward flange-shaped rotating side flange 8a for supporting and fixing the wheel on the outer peripheral surface. The outer diameter side bearing ring 3a is made of a quench-hardenable ferrous alloy such as medium carbon steel, and is arranged around the inner diameter side bearing ring 2a and concentrically with the inner diameter side bearing ring 2a. .. In the outer ring raceways 7c and 7d formed on the inner peripheral surface of the outer diameter side raceway 3a, the inner diameter dimension of the outer ring raceway 7d in the inner row is larger than the inner diameter dimension of the outer ring raceway 7c in the outer row.

玉４ａ、４ａは、内輪軌道５ｃ、５ｄと外輪軌道７ｃ、７ｄとの間に、両列毎にそれぞれ複数個ずつ、それぞれ保持器５２ａ、５２ｂに保持された状態で、転動自在に設けられている。又、内側列の玉４ａのピッチ円直径は、外側列の玉４ａのピッチ円直径よりも大きくなっている。 A plurality of balls 4a and 4a are provided between the inner ring raceways 5c and 5d and the outer ring raceways 7c and 7d, respectively, in a state of being held by the cages 52a and 52b, respectively, in a plural number for each row so as to be rollable. ing. The pitch circle diameter of the balls 4a in the inner row is larger than the pitch circle diameter of the balls 4a in the outer row.

又、外径側軌道輪３ａの内周面と内径側軌道輪２ａの外周面との間に存在する、内部空間（転動体設置空間）２６ａの軸方向両端開口を、シールリング２７ａ及びカバー２８ａにより塞いでいる。即ち、内部空間２６ａの軸方向内端開口部を、組み合わせ型等のシールリング２７ａにより塞いでいる。これに対し、内部空間２６ａの軸方向外端開口部は、径方向内側が軸方向に貫通していない内径側軌道輪２ａの軸方向外側面と共に、外径側軌道輪３ａの軸方向外端部に固定したカバー２８ａにより塞いでいる。 In addition, the seal ring 27a and the cover 28a are provided with openings at both axial ends of the internal space (rolling element installation space) 26a existing between the inner peripheral surface of the outer diameter side race ring 3a and the outer peripheral surface of the inner diameter side race ring 2a. It is blocked by. That is, the axially inner end opening of the internal space 26a is closed by the seal ring 27a of a combination type or the like. On the other hand, the axial outer end opening of the inner space 26a is the axial outer end of the outer diameter side race ring 3a together with the axial outer side surface of the inner diameter side race ring 2a whose radially inner side does not penetrate axially. It is closed by a cover 28a fixed to the section.

そして、本例の場合にも、外径側軌道輪３ａに設けられた回転側フランジ８ａを、複数の薄肉部９ａと、これら各薄肉部９ａよりも軸方向厚さ寸法が大きく且つ軸方向内側に突出（膨出）すると共に放射方向に伸長した複数の厚肉部１０ａとを、円周方向に関して交互に配置する事により構成している。又、薄肉部９ａは、厚肉部１０ａよりも径方向外方に延出する状態で設けられており、円周方向に隣り合う薄肉部９ａ同士は、これら薄肉部９ａの一部である薄肉連続部１１ａによって、厚肉部１０ａの径方向外側で円周方向に連続している。又、厚肉部１０ａの軸方向厚さ寸法Ｘは、薄肉部９ａ（薄肉連続部１１ａ）の軸方向厚さ寸法Ｙのおよそ２〜６倍程度（図示の例では２．５倍）に設定されている。 Even in the case of this embodiment, the outer diameter side of the rotation side flange 8a provided on the bearing ring 3 a, a plurality of the thin portion 9a, these larger axial thickness than the thin-wall part 9a and axially The plurality of thick-walled portions 10a that protrude (bulge) inward and extend in the radial direction are alternately arranged in the circumferential direction. Further, the thin-walled portions 9a are provided so as to extend radially outward from the thick-walled portions 10a, and the thin-walled portions 9a adjacent to each other in the circumferential direction are thin-walled portions 9a that are a part of these thin-walled portions 9a. Due to the continuous portion 11a, the thick portion 10a is circumferentially continuous outside in the radial direction. Further, the axial thickness dimension X of the thick portion 10a is set to about 2 to 6 times (2.5 times in the illustrated example) the axial thickness dimension Y of the thin portion 9a (thin continuous portion 11a). Has been done.

又、回転側フランジ８ａの円周方向等間隔複数箇所で、且つ、円周方向に関して厚肉部１０ａとそれぞれ整合する部分に、軸方向に貫通する状態で、取付孔４２ａを設けている。そして本例の場合にも、この取付孔４２ａを、軸方向外側の大径孔４３ａと、軸方向内側の雌ねじ孔４４ａとから構成している。 Further, mounting holes 42a are provided at a plurality of positions at equal intervals in the circumferential direction of the rotary side flange 8a, and in a portion that is aligned with the thick-walled portion 10a in the circumferential direction so as to penetrate in the axial direction. Also in the case of this example, the mounting hole 42a is composed of a large diameter hole 43a on the outer side in the axial direction and a female screw hole 44a on the inner side in the axial direction.

特に本例の場合には、大径孔４３ａの軸方向長さ寸法Ａを、薄肉部９ａの軸方向厚さ寸法Ｙよりも大きく設定している。これにより、大径孔４３ａと雌ねじ孔４４ａとの境界位置を、厚肉部１０ａのうちで薄肉連続部１１ａと径方向に重畳した重畳部１３ｃではなく、厚肉部１０ａのうちで薄肉連続部１１ａと径方向に重畳していない非重畳部１３ｄに位置させている。この為、雌ねじ孔４４ａは、厚肉部１０ａのうちの非重畳部１３ｄにのみ形成されており、重畳部１３ｃには形成されていない。 Particularly in the case of this example, the axial length dimension A of the large diameter hole 43a is set larger than the axial thickness dimension Y of the thin portion 9a. As a result, the boundary position between the large-diameter hole 43a and the female screw hole 44a is set at the thin-walled continuous portion of the thick-walled portion 10a rather than the thin-walled continuous portion 11a of the thick-walled portion 10a which is radially overlapped. It is located in the non-overlapping portion 13d that does not overlap with 11a in the radial direction. Therefore, the female screw hole 44a is formed only in the non-overlapping portion 13d of the thick wall portion 10a, and is not formed in the overlapping portion 13c.

以上の様な構成を有する本例の場合にも、前述した実施の形態の第１例の場合と同様に、雌ねじ孔４４ａを穿孔加工により形成する際に、この雌ねじ孔４４ａが途中で折れ曲がったり、雌ねじ孔４４ａの内径寸法が途中で変化したりする事を防止できる。従って、雌ねじ孔４４ａの精度（形状精度及び寸法精度）を十分に確保できる。
その他の構成及び作用効果に就いては、前記実施の形態の第１例の場合と同様である。 Also in the case of this example having the above-described configuration, as in the case of the first example of the above-described embodiment, when the female screw hole 44a is formed by drilling, the female screw hole 44a may be bent in the middle. It is possible to prevent the inner diameter of the female screw hole 44a from changing midway. Therefore, the accuracy (shape accuracy and dimensional accuracy) of the female screw hole 44a can be sufficiently ensured.
Other configurations and operational effects are the same as in the case of the first example of the above-described embodiment.

本発明は、実施の形態の各例に示した様に、従動輪用の車輪支持用転がり軸受ユニットだけでなく、駆動輪用の車輪支持用転がり軸受ユニットにも適用する事ができる。又、本発明は、前述した実施の形態の各例の構造を適宜組み合わせて実施する事もできる。 The present invention can be applied not only to the wheel supporting rolling bearing unit for the driven wheels but also to the wheel supporting rolling bearing unit for the driving wheels as shown in each of the embodiments. Further, the present invention can be implemented by appropriately combining the structures of the respective examples of the above-described embodiments.

１、１ａ、１ｂ 車輪支持用転がり軸受ユニット
２、２ａ 内径側軌道輪
３、３ａ 外径側軌道輪
４、４ａ 玉
５ａ〜５ｄ 内輪軌道
６ 静止側フランジ
７ａ〜７ｄ 外輪軌道
８、８ａ 回転側フランジ
９、９ａ 薄肉部
１０、１０ａ 厚肉部
１１、１１ａ 薄肉連続部
１２ 雌ねじ孔
１３ａ、１３ｃ 重畳部
１３ｂ、１３ｄ 非重畳部
１４ 外輪
１５ ハブ
１６ 玉
１７ａ、１７ｂ 外輪軌道
１８ 静止側フランジ
１８ａ ねじ孔
１９ ハブ本体
２０ 内輪
２１ａ、２１ｂ 内輪軌道
２２ 回転側フランジ
２３ 小径段部
２４ かしめ部
２５ａ、２５ｂ 保持器
２６、２６ａ 内部空間
２７ シールリング
２８ カバー
２９ 芯金
３０ シール材
３１ａ〜３１ｄ シールリップ
３２ 支持筒部
３３ 底板部
３４ シール材
３５ エンコーダ
３６ 支持環
３７ 根元部
３８ 肉厚変化部
３９ 薄肉部
４０ 厚肉部
４１ 薄肉連続部
４２、４２ａ 取付孔
４３、４３ａ 大径孔
４４、４４ａ 雌ねじ孔
４５ａ 重畳部
４５ｂ 非重畳部
４６ 透孔
４７ ねじ孔
４８ 凹部
４９ 主部
５０ 内輪素子
５１ かしめ部
５２ａ、５２ｂ 保持器 1, 1a, 1b Wheel support rolling bearing unit 2, 2a Inner diameter side race ring 3, 3a Outer diameter side race ring 4, 4a Balls 5a-5d Inner ring raceway 6 Stationary side flange 7a-7d Outer ring raceway 8, 8a Rotation side flange 9, 9a thin part 10, 10a thick part 11, 11a thin continuous part 12 female screw hole 13a, 13c overlapping part 13b, 13d non-overlapping part 14 outer ring 15 hub 16 ball 17a, 17b outer ring raceway 18 stationary side flange 18a screw hole 19 Hub body 20 Inner ring 21a, 21b Inner ring raceway 22 Rotation side flange 23 Small diameter step portion 24 Caulking portion 25a, 25b Cage 26, 26a Inner space 27 Seal ring 28 Cover 29 Core metal 30 Seal material 31a to 31d Seal lip 32 Support cylinder portion 33 Bottom plate part 34 Seal material 35 Encoder 36 Support ring 37 Root part 38 Wall thickness changing part 39 Thin part 40 Thick part 41 Thin continuous part 42, 42a Mounting hole 43, 43a Large diameter hole 44, 44a Female screw hole 45a Overlapping part 45b Non-overlapping portion 46 Through hole 47 Screw hole 48 Recessed portion 49 Main portion 50 Inner ring element 51 Caulking portion 52a, 52b Cage

Claims (1)

周面に静止側軌道を有し、使用時に懸架装置に支持固定されて回転しない静止側軌道輪と、
周面に回転側軌道を有すると共に、車輪を固定する為の外向フランジ状の回転側フランジを有し、使用時に回転する回転側軌道輪と、
前記静止側軌道と前記回転側軌道との間に転動自在に設けられた複数個の転動体と、
を備え、
前記回転側フランジは、全体が板状に構成され、複数の薄肉部と、これら各薄肉部よりも軸方向厚さ寸法が大きく且つ軸方向内側に突出した複数の厚肉部とが、円周方向に関して交互に設けられており、円周方向に隣り合う薄肉部同士が前記各厚肉部の径方向外側で連続しており、
円周方向に関して前記各厚肉部と整合する部分に、これら各厚肉部を軸方向に貫通する状態で、軸方向内側の雌ねじ孔と、この雌ねじ孔よりも内径寸法が大きく且つ無ねじ状である軸方向外側の大径孔とから構成される取付孔が設けられており、この大径孔の軸方向長さ寸法が前記各薄肉部の軸方向厚さ寸法よりも大きい
車輪支持用転がり軸受ユニット。 A stationary raceway ring that has a stationary side raceway on the circumferential surface and is not supported by the suspension device and is not rotated during use.
Having a rotating side raceway on the circumferential surface, and having a rotating side flange in the form of an outward flange for fixing the wheel, and a rotating side raceway wheel that rotates during use,
A plurality of rolling elements provided rotatably between the stationary side track and the rotating side track,
Equipped with
The rotation-side flange is formed in a plate shape as a whole, and has a plurality of thin-walled portions and a plurality of thick-walled portions that have axial thicknesses larger than the thin-walled portions and project inward in the axial direction. Are alternately provided with respect to the direction, adjacent to each other in the circumferential direction, the thin portions are continuous on the outer side in the radial direction of the thick portions,
A female screw hole on the inner side in the axial direction and an inner diameter larger than the female screw hole and non-threaded in a portion that matches each thick portion in the circumferential direction with each thick portion axially penetrating. Is provided with a large-diameter hole on the outside in the axial direction, and the axial length dimension of the large-diameter hole is larger than the axial thickness dimension of each thin-walled portion. Bearing unit.
JP2016211394A 2016-10-28 2016-10-28 Rolling bearing unit for wheel support Active JP6705363B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2016211394A JP6705363B2 (en) 2016-10-28 2016-10-28 Rolling bearing unit for wheel support
DE202017106535.9U DE202017106535U1 (en) 2016-10-28 2017-10-27 Rolling bearing unit for wheel bearing
CN201721413506.0U CN207634514U (en) 2016-10-28 2017-10-30 Wheel support roller bearing unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016211394A JP6705363B2 (en) 2016-10-28 2016-10-28 Rolling bearing unit for wheel support

Publications (3)

Publication Number Publication Date
JP2018071644A JP2018071644A (en) 2018-05-10
JP2018071644A5 JP2018071644A5 (en) 2019-06-20
JP6705363B2 true JP6705363B2 (en) 2020-06-03

Family

ID=60579624

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2016211394A Active JP6705363B2 (en) 2016-10-28 2016-10-28 Rolling bearing unit for wheel support

Country Status (3)

Country Link
JP (1) JP6705363B2 (en)
CN (1) CN207634514U (en)
DE (1) DE202017106535U1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6760149B2 (en) * 2016-08-30 2020-09-23 日本精工株式会社 Rolling bearing unit for wheel support
US11731456B2 (en) * 2019-05-24 2023-08-22 Aktiebolaget Skf Wheel hub bearing with radial stiffening
IT201900013584A1 (en) * 2019-08-01 2021-02-01 Skf Ab FLANGED INTERNAL RING FOR WHEEL HUB BEARINGS
JP2023011295A (en) * 2021-07-12 2023-01-24 Ntn株式会社 Vehicle wheel bearing device
CN113819213A (en) * 2021-09-22 2021-12-21 珠海格力电器股份有限公司 Harmonic reducer ware flexbile gear subassembly and harmonic reducer ware

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5641705B2 (en) * 2009-04-02 2014-12-17 Ntn株式会社 Wheel bearing device
JP2012051393A (en) 2010-08-31 2012-03-15 Nsk Ltd Rolling bearing unit for supporting wheel
JP2013067323A (en) * 2011-09-26 2013-04-18 Jtekt Corp Bearing device for axle
JP6007655B2 (en) * 2012-08-06 2016-10-12 株式会社ジェイテクト Wheel bearing device
JP6366233B2 (en) 2013-07-11 2018-08-01 Ntn株式会社 Wheel bearing device

Also Published As

Publication number Publication date
DE202017106535U1 (en) 2017-11-17
JP2018071644A (en) 2018-05-10
CN207634514U (en) 2018-07-20

Similar Documents

Publication Publication Date Title
JP6705363B2 (en) Rolling bearing unit for wheel support
JP2014126106A (en) Rolling bearing unit for supporting wheel
JP4345988B2 (en) Wheel bearing device
US10598226B2 (en) Bearing device for vehicle wheel
JP2017190865A (en) Hub unit bearing
JP6610441B2 (en) Rolling bearing unit for wheel support
JP2014013073A (en) Wheel bearing device
JP5045725B2 (en) Rolling bearing unit with rotational speed detector
JP2007162831A (en) Hub unit for driven wheel
JP2016109183A (en) Outer ring for rolling bearing unit, and rolling bearing unit for supporting wheel
JP2006275200A (en) Cover of rolling bearing device and rolling bearing device using this cover
JP2008110659A (en) Rolling bearing device for wheel
JP4419638B2 (en) Rolling bearing unit with rotational speed detector
JP2018034775A (en) Rolling bearing unit for supporting wheel
WO2017179400A1 (en) Hub unit bearing
JP4260055B2 (en) Wheel bearing device
JP2008014471A (en) Rolling bearing device with sensor
JP2022097522A (en) Hub unit bearing manufacturing method
JP2019035421A (en) Hub unit bearing with combination seal ring
JP4245249B2 (en) Bearing device
JP6968044B2 (en) Bearing device for wheels
WO2017033653A1 (en) Rolling bearing unit for wheel support
JP6744724B2 (en) Wheel bearing device
JP2019085018A (en) Hub unit bearing and hub unit bearing with braking rotating body
JP2022128123A (en) Bearing device for wheel

Legal Events

Date Code Title Description
A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20190516

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20190516

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20200414

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20200427

R150 Certificate of patent or registration of utility model

Ref document number: 6705363

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150