JPH06307438A - Wheel bearing - Google Patents
Wheel bearingInfo
- Publication number
- JPH06307438A JPH06307438A JP5095773A JP9577393A JPH06307438A JP H06307438 A JPH06307438 A JP H06307438A JP 5095773 A JP5095773 A JP 5095773A JP 9577393 A JP9577393 A JP 9577393A JP H06307438 A JPH06307438 A JP H06307438A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- space
- pair
- wheel
- 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.)
- Granted
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)
Abstract
Description
【0001】[0001]
【産業上の利用分野】この発明は、自動車等の車輪に用
いられる軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to bearings used for wheels of automobiles and the like.
【0002】[0002]
【従来の技術】図2に示すように、軸受外輪に相当する
ハブ(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。ハブ(1)の円筒部(4)の内径(5)には
複列のボール転走面(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)の外径には、ボール転走面
(6)に対向してそれぞれボール転走面(9)が形成さ
れている。両転走面(6、9)間に介在する複列のボー
ル(10)によりハブ(1)はスピンドル(7)に回転自
在に支承される。内輪(8)はスピンドル(7)の肩部
(11)と固定ナット(12)とに挟持されるが、軸受には
軸方向スキマが存在している。2. Description of the Related Art As shown in FIG. 2, a wheel (not shown) mounting flange (2) is integrally provided around the outer periphery of a hub (1) corresponding to a bearing outer ring, and a hub bolt (3) is fixed. Has been done. A double row ball rolling surface (6) is formed on the inner diameter (5) of the cylindrical portion (4) of the hub (1). On the other hand, the outer diameters of the pair of inner rings (8) fixed by press-fitting or inserting into the spindle (7) fixed to the vehicle body are respectively opposed to the ball rolling surface (6) and the ball rolling surface (9). ) Has been formed. The hub (1) is rotatably supported by the spindle (7) by the double rows of balls (10) interposed between the two rolling surfaces (6, 9). The inner ring (8) is sandwiched between the shoulder (11) of the spindle (7) and the fixed nut (12), but the bearing has an axial clearance.
【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方向スキマは負、すなわち所定
の予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初期スキマが設定されていた。In this type of bearing, it is advantageous to use the bearing with a negative axial clearance, that is, to apply a predetermined preload, from the viewpoints of rolling life and bearing rigidity of the bearing, but from the viewpoint of clearance management, Since it is difficult to measure the negative clearance, the initial clearance of the bearing is set in anticipation of a decrease in clearance by inserting or inserting the inner ring (8) into the spindle (7) and tightening of the nut (12). It was
【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、軸受の初期スキ
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、ハブ(外輪)(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 amount of preload is calculated in terms of life and rigidity, there is no means for realizing it, and the initial clearance of the bearing is set to near 0. I couldn't find a way to do it. Further, the hub (outer ring) (1) is integrally formed with the rolling surface (6), and the outer ring is not press-fitted into the housing or the like unlike a normal bearing. However, even if the clearance reduction (3 to 40 μm) due to the above-mentioned bearing assembly is expected, the optimum preload amount could not be obtained.
【0005】また、軸受組込み後のスキマを負にするた
めには初期スキマを測定可能な0以上を下限値とし上限
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。Further, in order to make the skimmer after the bearing is incorporated negative, the range of the upper limit must be made as small as possible, with 0 being the measurable initial skimmer, and the range of the upper limit must be made as small as possible. There was a management problem.
【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、外周にフランジが一体に周設され、円筒部内径に複
列の転走面が形成されている外輪と、各内輪の外径に上
記外輪の転走面に対向する転走面が形成され背面合わせ
されている一対の内輪と、外輪の転走面と内輪の転走面
との間に介在して外輪を回転自在に支承する複列の転動
体とを有し、上記一対の内輪の小端面間に所定のスキマ
が形成されている。SUMMARY OF THE INVENTION A bearing for a wheel according to the present invention has an outer ring in which a flange is integrally provided on the outer periphery, and a double row rolling surface is formed on the inner diameter of a cylindrical portion, and the outer diameter of each inner ring. A pair of inner rings having a rolling surface opposite to the rolling surface of the outer ring formed on the rear surface, and the outer ring rotatably supported by being interposed between the outer ring rolling surface and the inner ring rolling surface. And a predetermined gap is formed between the small end faces of the pair of inner rings.
【0007】[0007]
【作用】スキマ(δ)を所望の軸方向スキマに相当する
値に設定しておくことにより、組み付けに際してスキマ
(δ)が0になるまで一対の内輪(8)を締め付けると
最適予圧が得られる。このように軸受の初期スキマを負
スキマで保証することにより、組込み後のスキマを最適
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。By setting the clearance (δ) to a value corresponding to the desired axial clearance, optimum preload can be obtained by tightening the pair of inner rings (8) until the clearance (δ) becomes 0 during assembly. . In this way, by guaranteeing the initial clearance of the bearing with a negative clearance, the clearance after assembling can be set to an optimum value, and the bearing rigidity can be improved while maintaining the rolling life of the bearing.
【0008】[0008]
【実施例】図1に基づき本発明の実施例を説明する。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。Embodiment An embodiment of the present invention will be described with reference to FIG. It should be noted that the same parts as those of the above-described conventional technique 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 the bearing before assembly, and a gap (δ) corresponding to a desired axial clearance is formed between the small end faces (8a) of the pair of inner rings (8). Inner ring (8)
By press-fitting and tightening the fixing nut (12) (Fig. 1), until the clearance (δ) becomes 0, that is, the tightening torque increases rapidly, the pair of inner rings (8)
Tighten 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 the negative clearance can be accurately controlled by measuring the back pressure. As a method of measuring the clearance (δ),
For example, the method previously 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 bearing is lower than the outer bearing, and gradually decreases at the preload amount B as a boundary. 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 beyond that.
【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 an actual measurement value comparing the rigidity of the bearing (the present invention) in which the amount of preload is set to the value shown by B in FIG. 3 and the conventional bearing in which a slight amount of preload (less than B) is applied. . 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 type of wheel bearing has a unique effect in that the rigidity of the flange surface is increased even with respect to the moment load from the wheel due to the turning of the vehicle, and the problem of braking performance is reduced. Also, it can be seen that the rolling life can be maintained without being reduced as compared with the conventional bearing.
【0012】実施例のように複列アンギュラ玉軸受にお
いては、他の軸受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、トルクとスキマとの
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、
負スキマの保証が可能になったということは顕著な効果
を持つことになる。In the double-row angular contact ball bearing as in the embodiment, the absolute value of the starting torque of the bearing is smaller than that of other bearings such as the double-row tapered roller bearing, and it is difficult to guarantee the clearance due to the correlation between the torque and the clearance. Therefore, in this type of bearing, which cannot be expected to reduce the clearance by press fitting the outer ring,
The possibility of guaranteeing negative clearance will have a remarkable effect.
【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, without strictly controlling the tightening torque of the fixing nut as in the conventional bearing. All you have to do is to finish tightening with, and workability in assembling can be improved.
【0014】本発明は外輪回転形式の非駆動側車輪用軸
受に限らず、内輪回転形式、あるいは駆動側車輪用軸受
においても適用される。また、軸受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 applicable not only to the outer ring rotating type non-driving side wheel bearing but also to the inner ring rotating type or drive side wheel bearing. The bearing is not limited to the double-row angular contact ball bearing, and 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 construction, the present invention has the following effects.
【0016】車輪用軸受の剛性がアップし、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。The rigidity of the wheel bearing is increased, and the runout of the hub surface is reduced even when a large moment load is applied,
The swing of the brake rotor can also 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 defect rate can be reduced.
【0019】軸受の組込み作業性を向上できる。The workability of assembling the bearing can be improved.
【図1】本発明の実施例を示す組込み前の車輪用軸受の
縦断面図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FIG. 2 is a vertical sectional view of the wheel bearing in an assembled state.
【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FIG. 3 is a graph chart in which the total mileage life is plotted against the preload amount.
【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FIG. 4 is a graph diagram in which the bearing inclination angle is plotted against the moment load.
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 1 hub (outer ring) 2 flange 4 cylindrical part 5 inner diameter 6 rolling surface 8 inner ring 8a small end surface 9 rolling surface 10 ball (rolling element) δ gap
Claims (2)
部内径に複列の転走面が形成されている外輪と、各内輪
の外径に上記外輪の転走面に対向する転走面が形成され
背面合わせされている一対の内輪と、外輪の転走面と内
輪の転走面との間に介在して外輪を回転自在に支承する
複列の転動体とを有し、上記一対の内輪の小端面間に所
定のスキマが形成されている車輪用軸受。1. An outer ring having a flange integrally provided on the outer periphery thereof, and a double row rolling surface formed on the inner diameter of the cylindrical portion, and rolling that opposes the rolling surface of the outer ring on the outer diameter of each inner ring. A pair of inner rings whose surfaces are formed and which are back-to-back and a double row rolling element interposed between the rolling surface of the outer ring and the rolling surface of the inner ring to rotatably support the outer ring, A wheel bearing in which a predetermined clearance is formed between the small end faces of a pair of inner rings.
請求項1の車輪用軸受。2. The wheel bearing according to claim 1, wherein the bearing type is a double-row angular contact ball bearing.
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 true JPH06307438A (en) | 1994-11-01 |
JP2846545B2 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) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006349190A (en) * | 2006-09-22 | 2006-12-28 | Ntn Corp | Bearing device for drive axle and its manufacturing method |
JP2009503377A (en) * | 2005-07-27 | 2009-01-29 | ギュデル グループ アーゲー | Linear guide |
DE202014105452U1 (en) | 2013-11-13 | 2015-03-11 | Nsk Ltd. | rolling bearing unit |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6436722U (en) * | 1987-08-28 | 1989-03-06 |
-
1993
- 1993-04-22 JP JP5095773A patent/JP2846545B2/en not_active Expired - Lifetime
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6436722U (en) * | 1987-08-28 | 1989-03-06 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009503377A (en) * | 2005-07-27 | 2009-01-29 | ギュデル グループ アーゲー | Linear guide |
JP2006349190A (en) * | 2006-09-22 | 2006-12-28 | Ntn Corp | Bearing device for drive axle and its manufacturing method |
JP4607081B2 (en) * | 2006-09-22 | 2011-01-05 | Ntn株式会社 | Drive axle bearing device |
DE202014105452U1 (en) | 2013-11-13 | 2015-03-11 | Nsk Ltd. | rolling bearing unit |
Also Published As
Publication number | Publication date |
---|---|
JP2846545B2 (en) | 1999-01-13 |
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