JP2846545B2 - Wheel bearings - Google Patents

Wheel bearings

Info

Publication number
JP2846545B2
JP2846545B2 JP5095773A JP9577393A JP2846545B2 JP 2846545 B2 JP2846545 B2 JP 2846545B2 JP 5095773 A JP5095773 A JP 5095773A JP 9577393 A JP9577393 A JP 9577393A JP 2846545 B2 JP2846545 B2 JP 2846545B2
Authority
JP
Japan
Prior art keywords
bearing
rolling
inner ring
rolling surface
clearance
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.)
Expired - Lifetime
Application number
JP5095773A
Other languages
Japanese (ja)
Other versions
JPH06307438A (en
Inventor
弘二 佐橋
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.)
ENU TEI ENU KK
Original Assignee
ENU TEI ENU KK
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=14146810&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=JP2846545(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by ENU TEI ENU KK filed Critical ENU TEI ENU KK
Priority to JP5095773A priority Critical patent/JP2846545B2/en
Publication of JPH06307438A publication Critical patent/JPH06307438A/en
Application granted granted Critical
Publication of JP2846545B2 publication Critical patent/JP2846545B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2229/00—Setting preload
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Measuring Arrangements Characterized By The Use Of Fluids (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明が属する技術分野】 この発明は、自動車等の車
輪に用いられる車輪用軸受に関する。TECHNICAL FIELD The present invention relates to a wheel bearing used for a wheel of an automobile or the like.

【０００２】[0002]

【従来の技術】 図２は自動車の車輪用軸受として適用
された内輪分割型複列転がり軸受の、所定個所に組み付
けた状態を示したものである。軸受外輪に相当するハブ
または外方部材（１）の外周には車輪（図示せず）取付
け用フランジ（２）が一体に周設され、ハブボルト
（３）が固着されている。外方部材（１）の円筒部
（４）の内周面（５）には複列の転走面（６）が形成さ
れている。一方、車体に固定されるスピンドル（７）に
圧入または挿入して固定される一対の内輪（８）の外周
面には、外方部材の転走面（６）に対向してそれぞれ転
走面（９）が形成されている。両転走面（６，９）間に
転動自在に介在する複列の転動体つまりここではボール
（１０）により外方部材（１）がスピンドル（７）に回
転自在に支承される（外輪回転形式）。内輪（８）はス
ピンドル（７）の肩部（１１）と固定ナット（１２）と
に挟持される。2. Description of the Related Art FIG. 2 shows an inner ring split type double row rolling bearing applied as a wheel bearing for an automobile in a state where it is assembled at a predetermined position. A hub (not shown) mounting flange (2) is integrally provided around the hub or outer member (1) corresponding to the bearing outer ring, and a hub bolt (3) is fixed thereto. A double-row rolling surface (6) is formed on the inner peripheral surface (5) of the cylindrical portion (4) of the outer member (1). On the other hand, the outer peripheral surfaces of a pair of inner races (8) which are press-fitted or inserted into and fixed to a spindle (7) fixed to the vehicle body have rolling surfaces opposed to the rolling surface (6) of the outer member. (9) is formed. An outer member (1) is rotatably supported by a spindle (7) by a double row of rolling elements interposed rotatably between the two rolling surfaces (6, 9), ie, a ball (10) here (outer ring). Rotation format). The inner ring (8) is clamped between the shoulder (11) of the spindle (7) and the fixing nut (12).

【０００３】 この種の軸受においては、軸受の転動寿
命、軸受剛性の面から、軸受スキマとりわけアキシャル
スキマは負、すなわち所定の与圧を掛けて使用する方が
有利であるが、スキマ管理の面からは、負のスキマを測
定することは困難なため、内輪（８）をスピンドル
（７）に圧入または挿入することによるスキマ減少やナ
ット（１２）の締付けによるスキマ減少を見込んで軸受
の内部スキマ（組込み前の状態における軸受スキマ）が
設定されていた。In this type of bearing, in view of the rolling life and the bearing rigidity of the bearing, it is advantageous to use the bearing gap, especially the axial gap, negatively, that is, to apply a predetermined pressurization. Since it is difficult to measure the negative clearance from the surface, the clearance inside the bearing is reduced in consideration of the clearance reduction by press-fitting or inserting the inner ring (8) into the spindle (7) and the clearance reduction by tightening the nut (12). The clearance (bearing clearance before assembly) has been set.

【０００４】[0004]

【発明が解決しようとする課題】 従来の軸受では、寿
命および剛性の面から最適予圧量というものが算出され
ても、それを実現するための手段がなく、軸受の内部ス
キマを０近傍に設定する以外に方法は見出せなかった。
さらに、外方部材（１）には転走面（６）が一体に形成
されており、通常の軸受のようにハウジング等に外輪を
圧入する形式ではないため、圧入によるスキマ減少とい
う現象はなく、前述の軸受組込みによるスキマ減少（３
〜４０μｍ）を見込んだとしても、最適な予圧量を得る
ことはできなかった。In the conventional bearing, even if the optimum preload amount is calculated from the viewpoint of life and rigidity, there is no means for realizing it, and the internal clearance of the bearing is set to near zero. I couldn't find any way but to do it.
Furthermore, since the rolling surface (6) is formed integrally with the outer member (1) and the outer ring is not press-fitted into a housing or the like as in a normal bearing, there is no phenomenon of clearance reduction due to press-fitting. , The clearance reduction by incorporating the bearing described above (3.
４０40 μm), it was not possible to obtain the optimal preload amount.

【０００５】 また、組込み後の軸受スキマを負にする
ためには、内部スキマの設定値について、測定可能な０
以下を下限値とし、かつ、上限値の範囲を極力小さくし
なければならないことから、不良率が増大するなど品質
管理上問題があった。[0005] Further, in order to make the bearing clearance after assembly negative, it is necessary to set a measurable zero value for the internal clearance.
Since the following should be set as the lower limit and the range of the upper limit should be made as small as possible, there is a problem in quality control such as an increase in the defective rate.

【０００６】[0006]

【課題を解決するための手段】 この発明の車輪用軸受
は、車輪取付け用フランジと複列の転走面を備えた外方
部材と、転走面を備えた背面合わせの一対の内輪と、外
輪の転走面と内輪の転走面との間に転動自在に介在する
複列の転動体とを有し、前記外方部材と内輪と転動体を
組み合わせたアセンブリのアキシャルスキマが０の状態
のときに前記内輪の小端面間に寸法管理されたスキマを
形成させたものである。この車輪用軸受は、車両に組み
込み内輪の小端面同士を突き合わせた状態で、転動体と
転走面との間に寸法管理された負スキマが形成される。
組込み前の状態における内輪小端面間のスキマ（δ）の
値、すなわち、外方部材と内輪と転動体のアセンブリの
アキシャルスキマが０の状態のときの内輪小面間の寸法
は、内輪小端面同士を突き合わせたときの負のアキシャ
ルスキマの値に相当する。そして、そのスキマ（δ）の
寸法は、そこから排出されるエアーの背圧と相関関係に
あり、当該背圧の計測値に基づいて求めることができ
る。したがって、スキマ（δ）を所望のアキシャルスキ
マに相当する値に設定しておくことにより、軸受を車両
の所定個所に組み込んでスキマ（δ）が０になるまで、
つまり内輪小端面同士が当接するまで締め付けるだけで
最適予圧を付与することができる。このように、車両に
組み込んだ状態で確実に所望の負スキマが得られるよう
にすることで、予圧量を最適値に設定することができ、
軸受の転動寿命を維持しつつ、軸受剛性を向上させるこ
とができる。Means for Solving the Problems A wheel bearing of the present invention comprises: an outer member having a wheel mounting flange and a double-row rolling surface; a pair of back-aligned inner rings having a rolling surface; A double-row rolling element rotatably interposed between the rolling surface of the outer ring and the rolling surface of the inner ring, wherein an axial skimmer of an assembly in which the outer member, the inner ring and the rolling element are combined is 0 In the state, a gap whose size is controlled is formed between the small end faces of the inner ring. This wheel bearing is built into a vehicle, and a small gap is formed between the rolling element and the rolling surface in a state where the small end faces of the inner ring are abutted against each other.
The value of the clearance (δ) between the inner ring small end faces in the state before assembly, that is, the dimension between the inner ring small faces when the axial clearance of the assembly of the outer member, the inner ring and the rolling elements is 0, is the inner ring small end face. This corresponds to the value of the negative axial gap at the time of matching each other. The dimension of the gap (δ) is correlated with the back pressure of the air discharged from the gap, and can be obtained based on the measured value of the back pressure. Therefore, by setting the clearance (δ) to a value corresponding to a desired axial clearance, the bearing is assembled at a predetermined position of the vehicle and the clearance (δ) becomes zero until the clearance (δ) becomes zero.
That is, the optimum preload can be applied only by tightening until the inner ring small end faces come into contact with each other. In this way, by ensuring that a desired negative clearance is obtained in a state where the preload is incorporated in the vehicle, the preload amount can be set to an optimum value,
The bearing rigidity can be improved while maintaining the rolling life of the bearing.

【０００７】 上記車輪用軸受の外方部材に転走面を一
体に形成した場合には、外輪の圧入によるスキマ減少が
望めないため、内輪小端面同士を突き合わせるだけで所
望の負スキマが得られるようにしたことの有利さが顕著
にあらわれる。また、複列アンギュラ玉軸受は他の軸受
形式たとえば複列円すいころ軸受に比べて軸受の起動ト
ルクの絶対値が小さいことから、固定ナットによる締付
けトルクに基づいて予圧を正確に管理することは困難で
あり、それゆえ、ここでも内輪小端面同士を突き合わせ
るだけで所望の負スキマが得られる有利さが顕著なもの
となる。In the case where the rolling surface is formed integrally with the outer member of the above-described wheel bearing, a reduction in the clearance due to the press-fitting of the outer ring cannot be expected. Therefore, a desired negative clearance can be obtained only by abutting the small inner ring end faces. The advantage of being able to do so is remarkable. In addition, double-row angular contact ball bearings have a smaller absolute value of the starting torque of the bearing than other bearing types, for example, double-row tapered roller bearings, so it is difficult to accurately control the preload based on the tightening torque of the fixed nut. Therefore, the advantage that the desired negative clearance can be obtained only by abutting the inner ring small end surfaces becomes remarkable.

【０００８】[0008]

【発明の実施の形態】図１に従って本発明の実施の形態
を説明する。なお、図２に示される既述の従来技術と同
じ部品には同じ番号を付し、説明を省略する。DETAILED DESCRIPTION OF THE INVENTION describing embodiments <br/> in Figure 1 therefore the present invention. Note that the same components as those of the above-described conventional technology shown in FIG.

【０００９】図１は組込み前の軸受を示しており、一対
の内輪（８）の小端面（8a）間には所望の軸方向スキマ
に相当するスキマ（δ）が形成されている。内輪（８）
の圧入および固定ナット（12）（図１）の締め付けによ
り、このスキマ（δ）が０になるまで、すなわち締付け
トルクが急激に増大するところまで、一対の内輪（８）
を締め付けて軸受の予圧を設定する。軸受の初期スキマ
はスキマ（δ）から排出されるエアーの背圧と相関があ
り、背圧を計測することにより負スキマを精度よく管理
することができる。スキマ（δ）の測定方法としては、
たとえば本出願人が先に特願平３−５７７８７号におい
て提案している方法を採用することができる。FIG. 1 shows a bearing before assembly, and a gap (δ) corresponding to a desired axial gap is formed between the small end faces (8a) of a pair of inner rings (8). Inner ring (8)
By press-fitting and tightening the fixing nut (12) (FIG. 1), the pair of inner rings (8) until the clearance (δ) becomes zero, that is, until the tightening torque sharply increases.
To set the bearing preload. The initial clearance of the bearing has a correlation with the back pressure of the air discharged from the clearance (δ), and by measuring the back pressure, the negative clearance can be managed accurately. As a method of measuring the gap (δ),
For example, a method proposed by the present applicant in Japanese Patent Application No. 3-57787 can be adopted.

【００１０】図３は予圧量に対する軸受の転動寿命（計
算値）を示す。この場合、インナー側軸受はアウター側
に比べ低く、予圧量Ｂを境に漸次減少してゆく。一方、
アウター側軸受は、０から漸次減少してゆく。この図か
ら判るように、軸受全体の寿命は、予圧量Ｂまではイン
ナー側軸受の寿命に支配され、それ以上は予圧量に比例
して減少する傾向を持っている。FIG. 3 shows the rolling life (calculated value) of the bearing with respect to the amount of preload. In this case, the inner-side bearing is lower than the outer-side bearing, and gradually decreases starting from the preload B. on the other hand,
The outer bearing gradually decreases from zero. As can be seen from this figure, the life of the entire bearing is dominated by the life of the inner bearing up to the preload amount B, and tends to decrease in proportion to the preload amount thereafter.

【００１１】図４は予圧量を図３のＢで示される値に設
定した軸受（本発明）と僅かに予圧（Ｂより小）を負荷
した従来の軸受との剛性を比較した実測値である。この
場合、予圧量アップによって軸受の剛性は約２５％アッ
プしており、初期の低剛性もない。この種の車輪用軸受
として車の旋回による車輪からのモーメント荷重に対し
てもフランジ面の剛性が高くなり、ブレーキ性能上の問
題も減少するという特有の効果がある。また、転がり寿
命の点でも、従来軸受と比べ減少せず維持できることが
判る。FIG. 4 is a measured value comparing the rigidity of a bearing (the present invention) in which the amount of preload is set to the value indicated by B in FIG. 3 with that of a conventional bearing slightly loaded with a preload (smaller than B). . In this case, the rigidity of the bearing is increased by about 25% by increasing the preload amount, and there is no initial low rigidity. This kind of wheel bearing has a specific effect that the rigidity of the flange surface is increased even with a moment load from the wheel due to the turning of the car, and the problem on the braking performance is reduced. Also, it can be seen that the rolling life can be maintained without decreasing compared to the conventional bearing.

【００１２】 図面に例示した軸受形式（複列アンギュ
ラ玉軸受）においては、他の軸受形式たとえば複列円す
いころ軸受に比べ軸受の起動トルクの絶対値が小さく、
トルクとスキマの相関によるスキマの保証は困難である
から、外輪の圧入によるスキマ減少が望めないこの種の
軸受にあっては、内輪小端面同士を突き合わせるだけで
所望の負スキマが得られるという効果は格別顕著なもの
となる。In the bearing type illustrated in the drawings (double-row angular contact ball bearing), the absolute value of the starting torque of the bearing is smaller than other bearing types, for example, double-row tapered roller bearings.
Since it is difficult to guarantee the clearance based on the correlation between the torque and the clearance, in this type of bearing, where reduction in the clearance due to press-fitting of the outer ring cannot be expected, the desired negative clearance can be obtained only by abutting the small end faces of the inner ring. The effect is particularly pronounced.

【００１３】さらに、従来の軸受のように固定ナットの
締付けトルクを厳密に管理しなくても、内輪（８）の小
端面（8a）が当接した時点、すなわち絶対トルクが急激
に上昇した時点で締付けを終了するだけでよく、組込み
の上での作業性向上が図れる。Further, when the small end face (8a) of the inner ring (8) abuts, that is, when the absolute torque sharply rises, even if the tightening torque of the fixed nut is not strictly controlled unlike the conventional bearing. It is only necessary to end the tightening, and the workability upon assembling can be improved.

【００１４】 本発明は外輪回転形式の転がり軸受に限
らず、内輪回転形式の転がり軸受においても適用され
る。また、軸受形式は複列アンギュラ玉軸受に限らず複
列円すいころ軸受であってもよい。The present invention is not limited to the outer ring rolling type rolling bearing, but is also applied to an inner ring rotating type rolling bearing. The bearing type is not limited to a double-row angular contact ball bearing, but may be a double-row tapered roller bearing.

【００１５】[0015]

【発明の効果】以上の構成により、本発明には以下に挙
げる効果がある。With the above arrangement, the present invention has the following effects.

【００１６】剛性がアップし、たとえば車輪用軸受に適
用した場合、大きなモーメント荷重が付加されてもハブ
面の振れが小さくなり、ブレーキロータの振れも小さく
できる。[0016] The stiffness is up, for example, applied to the wheel bearing
When used, even if a large moment load is applied, the runout of the hub surface is reduced, and the runout of the brake rotor can be reduced.

【００１７】軸受の転がり寿命を維持しつつ軸受の剛性
アップが図れる。The rigidity of the bearing can be increased while maintaining the rolling life of the bearing.

【００１８】軸受初期スキマの範囲を大きくでき、不良
率を低減できる。The range of the initial clearance of the bearing can be increased, and the defective rate can be reduced.

【００１９】軸受の組込み作業性を向上できる。The workability of mounting the bearing can be improved.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施の形態を示す組込み前の車輪用軸
受の縦断面図である。 FIG. 1 is a vertical cross-sectional view of a wheel bearing before assembly, showing an embodiment of the present invention .

【図２】組み込んだ状態の車輪用軸受の縦断面図であ
る。 FIG. 2 is a vertical cross-sectional view of a wheel bearing of the state incorporating Der
You.

【図３】予圧量に対する総合走行距離寿命をプロットし
たグラフ図である。 FIG. 3 is a graph in which the total travel distance life is plotted against the amount of preload .

【図４】モーメント荷重に対する軸受傾き角をプロット
したグラフ図である。 FIG. 4 is a graph plotting a bearing inclination angle with respect to a moment load .

【符号の説明】[Explanation of symbols]

１ ハブ（外輪） ２ フランジ ４ 円筒部 ５ 内径 ６ 転走面 ８ 内輪 8a 小端面 ９ 転走面 10 ボール（転動体） δ スキマ Reference Signs List 1 hub (outer ring) 2 flange 4 cylindrical portion 5 inner diameter 6 rolling surface 8 inner ring 8a small end surface 9 rolling surface 10 ball (rolling element) δ

Claims (4)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】 車輪取付け用フランジと複列の転走面を
備えた外方部材と、転走面を備えた背面合わせの一対の
内輪と、外輪の転走面と内輪の転走面との間に転動自在
に介在する複列の転動体とを有し、前記外方部材と内輪
と転動体を組み合わせたアセンブリのアキシャルスキマ
が０の状態のときに前記内輪の小端面間に寸法管理され
たスキマを形成させた車輪用軸受。1. An outer member having a wheel mounting flange and a double row of rolling surfaces, a pair of back-to-back inner rings having a rolling surface, a rolling surface of an outer ring and a rolling surface of an inner ring. Between the small end faces of the inner ring when the axial gap of the assembly combining the outer member, the inner ring and the rolling element is zero. Wheel bearings with controlled gaps. 【請求項２】 車輪取付け用フランジと複列の転走面を
備えた外方部材と、転走面を備えた背面合わせの一対の
内輪と、外輪の転走面と内輪の転走面との間に転動自在
に介在する複列の転動体とを有し、車両に組み込み内輪
の小端面同士を突き合わせた状態で転動体と転走面との
間に寸法管理された負スキマが形成されている車輪用軸
受。2. An outer member having a wheel mounting flange and a double row of rolling surfaces, a pair of back-to-back inner rings having a rolling surface, a rolling surface of an outer ring and a rolling surface of an inner ring. And a double row of rolling elements interposed freely between the rolling elements, and a dimension-controlled negative gap is formed between the rolling elements and the rolling surface with the small end faces of the inner ring assembled against each other in the vehicle. Bearings for wheels. 【請求項３】 外方部材にフランジと複列の転走面が一
体に形成されている請求項１又は２の車輪用軸受。3. The wheel bearing according to claim 1, wherein the outer member is integrally formed with a flange and a double row rolling surface. 【請求項４】 軸受形式が複列アンギュラ玉軸受である
請求項１、２又は２の車輪用軸受。4. The wheel bearing according to claim 1, wherein the bearing type is a double-row angular contact ball bearing.
JP5095773A 1993-04-22 1993-04-22 Wheel bearings Expired - Lifetime JP2846545B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP5095773A JP2846545B2 (en) 1993-04-22 1993-04-22 Wheel bearings

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP5095773A JP2846545B2 (en) 1993-04-22 1993-04-22 Wheel bearings

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP8261006A Division JPH09105411A (en) 1996-10-01 1996-10-01 Bearing for wheel

Publications (2)

Publication Number Publication Date
JPH06307438A JPH06307438A (en) 1994-11-01
JP2846545B2 true JP2846545B2 (en) 1999-01-13

Family

ID=14146810

Family Applications (1)

Application Number Title Priority Date Filing Date
JP5095773A Expired - Lifetime JP2846545B2 (en) 1993-04-22 1993-04-22 Wheel bearings

Country Status (1)

Country Link
JP (1) JP2846545B2 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1748200A1 (en) * 2005-07-27 2007-01-31 Güdel Group Ag Linear guide
JP4607081B2 (en) * 2006-09-22 2011-01-05 Ｎｔｎ株式会社 Drive axle bearing device
JP2015094440A (en) 2013-11-13 2015-05-18 日本精工株式会社 Rolling bearing unit

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6436722U (en) * 1987-08-28 1989-03-06

Also Published As

Publication number Publication date
JPH06307438A (en) 1994-11-01

Similar Documents

Publication Publication Date Title
US6428214B2 (en) Wheel bearing unit
US6280093B1 (en) Wheel supporting structure
US8021052B2 (en) Sensor-equipped bearing for wheel
JP2002323056A (en) Wheel bearing device
JP2003074571A (en) Srolling bearing unit for driving wheel and driving unit for car wheel
US6109793A (en) Rolling bearing unit with rotational speed sensor
JP2000227132A (en) Wheel bearing device with brake rotor
JP3639421B2 (en) Preload measurement method for double row rolling bearings
JP2846545B2 (en) Wheel bearings
KR20050088143A (en) Hub unit with sensor
JP2601238Y2 (en) Sealing device for wheel bearings
JP3969142B2 (en) Rolling bearing unit for wheel support
JP2001311442A (en) Brake rotor and wheel bearing device provided with the same
JP2009156450A (en) Bearing device for wheel
JP2002019405A (en) Wheel bearing device
WO2024043123A1 (en) Wheel bearing device
JPH0527329Y2 (en)
JP3306918B2 (en) Wheel speed detector
JP2000356646A (en) Rolling bearing unit with rotation speed detection device
JP4236832B2 (en) Wheel bearing device
JP2008168665A (en) Bearing device for wheel
JPH09105411A (en) Bearing for wheel
JP3097674B2 (en) Rolling bearing unit with rotation speed detector
JPWO2003064184A1 (en) Wheel bearing unit
JPH0673459U (en) Wheel support device

Legal Events

Date Code Title Description
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 19980922