JP2004108487A - Roller bearing - Google Patents

Roller bearing Download PDF

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Publication number
JP2004108487A
JP2004108487A JP2002271665A JP2002271665A JP2004108487A JP 2004108487 A JP2004108487 A JP 2004108487A JP 2002271665 A JP2002271665 A JP 2002271665A JP 2002271665 A JP2002271665 A JP 2002271665A JP 2004108487 A JP2004108487 A JP 2004108487A
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Japan
Prior art keywords
peripheral surface
inner peripheral
slinger
ring
rolling bearing
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JP2002271665A
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Japanese (ja)
Inventor
Koichi Goto
後藤　耕一
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NSK Ltd
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NSK Ltd
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Priority to JP2002271665A priority Critical patent/JP2004108487A/en
Publication of JP2004108487A publication Critical patent/JP2004108487A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Abstract

<P>PROBLEM TO BE SOLVED: To provide a successful roller bearing capable of obtaining sufficient water-proof and simultaneously preventing a slinger from turning in unison during high speed rotation. <P>SOLUTION: The roller bearing 30 is configured so that a plurality of balls 3 make it possible to roll in circumferential direction and is interposed between an outer ring 31 and an inner ring 32, and simultaneously an end opening of axial direction is covered by the slinger 50 along with a sealing plate 35. An attached groove 40 which is formed on inner peripheral surface of end of the inner ring 12 includes annular inner peripheral surface 41 eccentric to axis while simultaneously the slinger 50 includes a circular ring 51 covering the end opening and a cylindrical part 52 formed on inner peripheral edge of the circular ring 51. On outer peripheral surface of the cylindrical part 52 which is fixed to fit-in concentric with the inner ring 32 with respect to the annular inner peripheral surface 41 of the attached groove 40, an engaged protuberance 53 is protrusively formed in radially outward direction in accordance with eccentric amount of the annular inner peripheral surface 41 and is press fitted on the annular inner peripheral surface 41. <P>COPYRIGHT: (C)2004,JPO

Description

【０００１】
【発明の属する技術分野】
本発明は転がり軸受に関し、特に、オルタネータ等の自動車の電装補機軸受に使用され、耐水性を要求される転がり軸受の改良に関する。
【０００２】
【従来の技術】
従来、オルタネータ等の自動車の電装補機軸受に使用され、耐水性を要求される転がり軸受としては、高密封の接触シール軸受や端部開口がシール部材及びスリンガにより覆われた転がり軸受が使用されている（例えば、特許文献１参照）。
例えば図５に示した転がり軸受１０は、外輪１と内輪２との間に複数の玉３が保持器４を介して周方向に転動可能に介装されており、外輪１の軸線方向の端部内周面にはシール部材として接触型のシール板５が取り付けられている。
【０００３】
そして、この転がり軸受１０をオルタネータの軸受として使用する場合には、内輪２をオルタネータの回転軸７に外嵌固定すると共に、該回転軸７に嵌め込んだスリンガ６を内輪２の端面近傍に配置して該スリンガ６で転がり軸受１０の端部開口を覆う。
これにより、シール板５のリップ部５ａと内輪２との摺接部に水等が直接かかるのを防止すると共に、回転軸７と共に回転するスリンガ６の遠心力により該スリンガ６に付着した水等を吹き飛ばし、前記摺接部に水等が入り込むのを防止している。
【０００４】
一方、図６に示した転がり軸受２０は、外輪１１と内輪１２との間に複数の玉３が保持器４を介して周方向に転動可能に介装されており、外輪１１の軸線方向の端部内周面にはシール部材として接触型のシール板５が取り付けられている。また、内輪１２の端部外周面にはスリンガ１６の円筒部１８が圧入等により外嵌固定されており、該円筒部８の外端部には転がり軸受２０の端部開口を覆う円輪部１７がシール板１５と転がり軸受２０の端面との間に位置して設けられている。
【０００５】
そして、この転がり軸受２０をオルタネータの軸受として使用する場合には、内輪１２をオルタネータの回転軸７に外嵌固定することにより、スリンガ１６の円輪部１７によってシール板１５のリップ部１５ａと内輪１２との摺接部に水等が直接かかるのを防止すると共に、内輪１２と伴に回転するスリンガ１６の遠心力により該スリンガ１６の円輪部１７に付着した水を吹き飛ばして前記摺接部へ水等が入り込むのを防止している。
【０００６】
【特許文献１】
特開２０００−１８２６０号公報（第３−４頁、第１図）
【０００７】
【発明が解決しようとする課題】
ところが、図５に示した転がり軸受１０においては、スリンガ６が転がり軸受１０の内輪２の端面近傍に配置されているため、シール板５とスリンガ６との間のすき間寸法が大きくなって十分な耐水性が得られない場合がある。
一方、図６に示した転がり軸受２０では、スリンガ１６の円筒部１８が内輪１２の端部外周面に圧入等により外嵌固定され、且つ転がり軸受２０の端部開口を覆う円輪部１７がシール板１５と転がり軸受２０の端面との間に位置して設けられるため、シール板１５とスリンガ１６の円輪部１７との間のすき間寸法を小さくすることができる。
【０００８】
しかしながら、今後さらにオルタネータの回転軸７の回転速度が高速化した場合、内輪１２の端部外周面に圧入等により外嵌固定された前記円筒部１８が遠心力により拡径方向に変形し、スリンガ１６が高速回転する内輪２に対して連れ回りを起こす可能性がある。
従って、本発明の目的は上記課題を解消することに係り、十分な耐水性を得ることができると共に、高速回転時のスリンガの連れ回りを防止することができる良好な転がり軸受を提供することである。
【０００９】
【課題を解決するための手段】
本発明の上記目的は、外輪と内輪との間に複数の転動体が周方向に転動可能に介装されると共に、軸線方向の少なくとも一方の端部開口がシール部材と伴にスリンガにより覆われる転がり軸受であって、
前記内輪の少なくとも一方の端部内周面に形成された取付溝が、軸線に対して偏心した円環状内周面を有すると共に、前記スリンガが、前記端部開口を覆う円輪部と、該円輪部の内周縁に形成された円筒部とを有しており、
前記取付溝の円環状内周面に対して前記内輪と同心に内嵌固定される前記円筒部の外周面には、該円環状内周面の偏心量に応じて係合突起が径方向外方に突出形成され、前記円環状内周面に圧入されることを特徴とする転がり軸受により達成される。
【００１０】
上記構成によれば、スリンガの円筒部が、内輪の端部内周面に形成された取付溝の円環状内周面に対して前記内輪と同心に内嵌固定されると共に、軸線に対して偏心した前記円環状内周面の偏心量に応じて前記円筒部の外周面に突出形成された係合突起が、該円環状内周面に圧入される。
そこで、回転軸が高速回転した場合にも、スリンガの円筒部が遠心力により拡径方向に変形することはなく、該円筒部の係合突起が取付溝の偏心した円環状内周面に係止されるので、スリンガは連れ回りが防止され、確実に固定される。
【００１１】
尚、好ましくは前記円輪部の板厚に相当する逃げ部が、前記取付溝に隣接する内輪端部に形成されている。
この場合、スリンガの円輪部を逃げ部に補完的に取り付けることで、該円輪部の外側面を外輪の端面と略面一とすることができ、スリンガを含めた転がり軸受の軸方向幅を短くすることができる。しかも、シール板とスリンガの円輪部との間のすき間寸法も小さくすることができるので、十分な耐水性を得ることができる。
【００１２】
又、好ましくは前記内輪が、オルタネータの回転軸に外嵌固定されることにより、今後被水環境等の条件が厳しくなる一方で信頼性の要求が高くなる自動車のオルタネータの転がり軸受としてに好適に使用することができる。
【００１３】
【発明の実施の形態】
以下、添付図面に基づいて本発明の一実施形態に係る転がり軸受を詳細に説明する。
図１は本発明の一実施形態に係る転がり軸受の要部断面図、図２は図１に示した取付溝の円環状内周面に対するスリンガの円筒部の配置を軸方向端部側から見た説明図、図３は図２のＡ−Ａ線矢視断面図である。
【００１４】
本発明の一実施形態に係る転がり軸受３０は、図１に示したように、外輪３１と内輪３２との間に複数の玉３が保持器４を介して周方向に転動可能に介装されており、外輪３１の軸線方向の端部内周面にはシール部材として接触型のシール板３５が取り付けられると共に、内輪３２の端部内周面に形成された取付溝４０にはスリンガ５０が取り付けられている。
【００１５】
前記シール板３５は、例えば円輪状の芯金３６にゴム等のシール材３７を加硫接着等により一体に成形したものを用いており、シール材３７の内径部はリップ部３５ａとされて内輪３２の軸線方向の端部に形成された段部３８の側面に摺接している。
【００１６】
前記内輪３２の端部内周面に形成された取付溝４０は、内輪３２の軸線に対して偏心した円環状内周面４１を有している。
前記スリンガ５０は、転がり軸受３０の端部開口を覆う円輪部５１と、該円輪部５１の内周縁に形成された円筒部５２とを有しており、前記取付溝４０の円環状内周面４１に対して前記内輪３２と同心に内嵌固定される該円筒部５２の外周面には、図２及び図３に示したように、前記円環状内周面４１の偏心量に応じて係合突起５３が径方向外方に突出形成されている。
【００１７】
そして、前記係合突起５３を前記円環状内周面４１の径方向の深さが最も深い位置（偏心が最大の位置）に圧入することにより、前記円筒部５２が取付溝４０の円環状内周面４１に内輪３２と同心に内嵌固定される。
又、前記円輪部５１の板厚に相当する逃げ部３４が、前記取付溝４０に隣接する内輪３２の端部に形成されており、スリンガ５０の円輪部５１を該逃げ部３４に補完的に取り付けることで、該円輪部５１の外側面を外輪３１の端面と略面一とすることができ、スリンガ５０を含めた転がり軸受３０の軸方向幅を短くすることができる。しかも、シール板３５とスリンガ５０の円輪部５１との間のすき間寸法も小さくすることができるので、十分な耐水性を得ることができる。
【００１８】
更に、本実施形態のスリンガ５０における円輪部５１の外周部は、軸方向内側に屈曲されてシール板３５に近接配置されており、該円輪部５１の外周端はシール板３５のシール材３７に軸方向外方に突出して設けられた環状突起３７ａの内周面に近接配置されている。
【００１９】
そして、この転がり軸受３０をオルタネータ等に使用した場合には、内輪３２をオルタネータの回転軸（図示せず）に外嵌固定することにより、スリンガ５０の円輪部５１によってシール板３５のリップ部３５ａと内輪３２との摺接部に水等が直接かかるのを防止すると共に、内輪３２と共に回転するスリンガ５０の遠心力により該スリンガ５０の円輪部５１に付着した水を吹き飛ばして前記摺接部へ水等が入り込むのを防止することができる。
【００２０】
即ち、本実施形態に係る転がり軸受３０によれば、スリンガ５０の円筒部５２が、内輪３２の端部内周面に形成された取付溝４０の円環状内周面４１に対して前記内輪３２と同心に内嵌固定されると共に、軸線に対して偏心した前記円環状内周面４１の偏心量に応じて前記円筒部５２の外周面に突出形成された係合突起５３が、該円環状内周面４１に圧入される。
【００２１】
そこで、回転軸が高速回転した場合にも、スリンガ５０の円筒部５２が遠心力により拡径方向に変形することはなく、該円筒部５２の係合突起５３が取付溝４０の偏心した円環状内周面４１に係止されるので、スリンガ５０は連れ回りが防止され、確実に固定される。
従って、今後被水環境等の条件が厳しくなる一方で信頼性の要求が高くなる自動車のオルタネータに好適に使用できる転がり軸受３０を提供することができる。
【００２２】
図４は、図５に示した従来の転がり軸受１０にスリンガ６を組み合わせたものを従来例とし、図１に示した本実施形態の転がり軸受３０を本発明例として、それぞれ転がり軸受内への水浸入量の比較試験を行った結果を示したものである。
尚、前記試験は、スリンガ以外の転がり軸受の仕様（６２０２サイズ）を同一とし、回転数１５００ｍｉｎ−１、注水量２００ｃｃ／ｍｉｎ（スリンガ面直水）で２０時間行った。
図４から明らかなように、本発明例の転がり軸受３０は、軸受内への水の浸入がなく、水浸入量が１００ｍｇの従来例に対して耐水性能が大幅に向上した。
【００２３】
尚、本発明の転がり軸受における内外輪、転動体、シール部材、スリンガ、取付溝及び係合突起等の構成は、上記実施形態の構成に限定されるものではなく、本発明の趣旨に基づいて種々の形態を採りうることは言うまでもない。
例えば、上記実施形態においては転がり軸受として玉軸受を用いたが、ころ軸受等の他の形式の転がり軸受にも応用でき、シール部材として非接触型のシールドを用いることもできる。
【００２４】
【発明の効果】
以上、上述した本発明の転がり軸受によれば、スリンガの円筒部が、内輪の端部内周面に形成された取付溝の円環状内周面に対して前記内輪と同心に内嵌固定されると共に、軸線に対して偏心した前記円環状内周面の偏心量に応じて前記円筒部の外周面に突出形成された係合突起が、該円環状内周面に圧入される。
そこで、回転軸が高速回転した場合にも、スリンガの円筒部が遠心力により拡径方向に変形することはなく、該円筒部の係合突起が取付溝の偏心した円環状内周面に係止されるので、スリンガは連れ回りが防止され、確実に固定される。
従って、十分な耐水性を得ることができると共に、高速回転時のスリンガの連れ回りを防止することができる良好な転がり軸受を提供できる。
【図面の簡単な説明】
【図１】本発明の一実施形態に係る転がり軸受の要部断面図である。
【図２】図１に示した取付溝の円環状内周面に対するスリンガの円筒部の配置を軸方向端部側から見た説明図である。
【図３】図２のＡ−Ａ線矢視断面図である。
【図４】従来例と本発明例とにおける転がり軸受内への水浸入量の比較を示すグラフ図である。
【図５】従来の転がり軸受の要部断面図である。
【図６】従来の他の転がり軸受の要部断面図である。
【符号の説明】
３　玉（転動体）
３０　転がり軸受
３１　外輪
３２　内輪
３４　逃げ部
４０　取付溝
４１　円環状内周面
５０　スリンガ
５１　円輪部
５２　円筒部
５３　係合突起[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a rolling bearing, and more particularly to an improvement in a rolling bearing which is used for an electric auxiliary accessory bearing of an automobile such as an alternator and requires water resistance.
[0002]
[Prior art]
Conventionally, as a rolling bearing which is used for an electric component auxiliary bearing of an automobile such as an alternator and requires water resistance, a highly sealed contact seal bearing and a rolling bearing whose end opening is covered with a sealing member and a slinger are used. (For example, see Patent Document 1).
For example, in the rolling bearing 10 shown in FIG. 5, a plurality of balls 3 are interposed between the outer ring 1 and the inner ring 2 so as to be able to roll in the circumferential direction via the retainer 4. A contact-type sealing plate 5 is attached to the inner peripheral surface of the end as a sealing member.
[0003]
When the rolling bearing 10 is used as a bearing for an alternator, the inner ring 2 is externally fixed to the rotating shaft 7 of the alternator, and the slinger 6 fitted to the rotating shaft 7 is arranged near the end face of the inner ring 2. Then, the slinger 6 covers the end opening of the rolling bearing 10.
This prevents water or the like from directly splashing on the sliding contact portion between the lip portion 5a of the seal plate 5 and the inner ring 2, and water or the like adhered to the slinger 6 due to the centrifugal force of the slinger 6 rotating together with the rotating shaft 7. To prevent water and the like from entering the sliding contact portion.
[0004]
On the other hand, in the rolling bearing 20 shown in FIG. 6, a plurality of balls 3 are interposed between the outer ring 11 and the inner ring 12 so as to be rollable in the circumferential direction via the retainer 4. A contact-type sealing plate 5 is attached as a sealing member to the inner peripheral surface of the end portion. A cylindrical portion 18 of a slinger 16 is externally fitted and fixed to an outer peripheral surface of an end portion of the inner ring 12 by press-fitting or the like, and a circular ring portion covering an end opening of a rolling bearing 20 is provided at an outer end portion of the cylindrical portion 8. 17 is provided between the seal plate 15 and the end face of the rolling bearing 20.
[0005]
When this rolling bearing 20 is used as a bearing of an alternator, the inner ring 12 is externally fitted and fixed to the rotating shaft 7 of the alternator, so that the lip portion 15a of the seal plate 15 and the inner ring In addition to preventing water or the like from directly splashing on the sliding contact portion with the inner ring 12, the water attached to the circular ring portion 17 of the slinger 16 is blown off by the centrifugal force of the slinger 16 rotating with the inner ring 12, and the sliding contact portion is removed. Water is prevented from entering.
[0006]
[Patent Document 1]
JP-A-2000-18260 (pages 3-4, FIG. 1)
[0007]
[Problems to be solved by the invention]
However, in the rolling bearing 10 shown in FIG. 5, since the slinger 6 is disposed near the end face of the inner ring 2 of the rolling bearing 10, the clearance between the seal plate 5 and the slinger 6 becomes large, so that sufficient clearance is obtained. Water resistance may not be obtained in some cases.
On the other hand, in the rolling bearing 20 shown in FIG. 6, the cylindrical portion 18 of the slinger 16 is externally fitted and fixed to the outer peripheral surface of the end portion of the inner ring 12 by press fitting or the like, and the circular ring portion 17 covering the end opening of the rolling bearing 20 is formed. Since it is provided between the seal plate 15 and the end face of the rolling bearing 20, the clearance between the seal plate 15 and the ring portion 17 of the slinger 16 can be reduced.
[0008]
However, if the rotation speed of the rotating shaft 7 of the alternator is further increased in the future, the cylindrical portion 18 externally fitted and fixed to the outer peripheral surface of the end of the inner race 12 by press fitting or the like is deformed in the radially expanding direction by centrifugal force, and the slinger 16 may rotate with respect to the inner ring 2 rotating at high speed.
Therefore, an object of the present invention is to solve the above-mentioned problems, and to provide a good rolling bearing which can obtain sufficient water resistance and can prevent the slinger from rotating together at the time of high-speed rotation. is there.
[0009]
[Means for Solving the Problems]
The object of the present invention is to provide a vehicle including a plurality of rolling elements interposed between an outer ring and an inner ring so as to be able to roll in a circumferential direction, and at least one end opening in the axial direction covered by a slinger together with a seal member. Rolling bearing,
A mounting groove formed in at least one end inner peripheral surface of the inner ring has an annular inner peripheral surface eccentric to an axis, and the slinger covers the end opening; A cylindrical portion formed on the inner peripheral edge of the ring portion,
The outer peripheral surface of the cylindrical portion, which is fitted and fixed concentrically with the inner race with respect to the annular inner peripheral surface of the mounting groove, has an engagement projection on the outer periphery in the radial direction according to the amount of eccentricity of the annular inner peripheral surface. The rolling bearing is formed so as to protrude toward the inner side and is press-fitted into the annular inner peripheral surface.
[0010]
According to the above configuration, the cylindrical portion of the slinger is fitted and fixed concentrically with the inner ring with respect to the annular inner peripheral surface of the mounting groove formed on the inner peripheral surface of the end of the inner ring, and is eccentric with respect to the axis. An engagement projection formed on the outer peripheral surface of the cylindrical portion according to the eccentric amount of the annular inner peripheral surface is press-fitted into the annular inner peripheral surface.
Therefore, even when the rotating shaft rotates at a high speed, the cylindrical portion of the slinger does not deform in the radially expanding direction due to centrifugal force, and the engaging projection of the cylindrical portion engages with the eccentric inner peripheral surface of the mounting groove. Since the slinger is stopped, the slinger is prevented from rotating and is securely fixed.
[0011]
Preferably, a relief portion corresponding to a plate thickness of the circular ring portion is formed at an end of the inner ring adjacent to the mounting groove.
In this case, by complementarily attaching the ring portion of the slinger to the relief portion, the outer surface of the ring portion can be made substantially flush with the end surface of the outer ring, and the axial width of the rolling bearing including the slinger is provided. Can be shortened. In addition, since the clearance between the seal plate and the ring portion of the slinger can be reduced, sufficient water resistance can be obtained.
[0012]
Further, preferably, the inner ring is externally fixed to the rotating shaft of the alternator, so that it becomes suitable as a rolling bearing for an alternator of an automobile in which requirements for reliability will be increased while conditions such as a wet environment will be stricter in the future. Can be used.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a rolling bearing according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 is a sectional view of a main part of a rolling bearing according to an embodiment of the present invention, and FIG. 2 is a view of an arrangement of a cylindrical portion of a slinger with respect to an annular inner peripheral surface of a mounting groove shown in FIG. FIG. 3 is a sectional view taken along line AA of FIG.
[0014]
As shown in FIG. 1, a rolling bearing 30 according to an embodiment of the present invention includes a plurality of balls 3 interposed between an outer ring 31 and an inner ring 32 via a retainer 4 so as to be rollable in a circumferential direction. A contact-type sealing plate 35 is attached as a sealing member to an inner peripheral surface of an end portion of the outer ring 31 in the axial direction, and a slinger 50 is attached to a mounting groove 40 formed in the inner peripheral surface of the end portion of the inner ring 32. Have been.
[0015]
As the seal plate 35, for example, a seal material 37 such as rubber is integrally formed on a ring-shaped core metal 36 by vulcanization bonding or the like, and an inner diameter portion of the seal material 37 is formed as a lip portion 35a to form an inner ring. 32 is in sliding contact with a side surface of a step portion 38 formed at an axial end.
[0016]
The mounting groove 40 formed in the inner peripheral surface at the end of the inner race 32 has an annular inner peripheral surface 41 eccentric with respect to the axis of the inner race 32.
The slinger 50 has a ring portion 51 covering an end opening of the rolling bearing 30 and a cylindrical portion 52 formed on an inner peripheral edge of the ring portion 51. As shown in FIGS. 2 and 3, the outer peripheral surface of the cylindrical portion 52 which is fitted and fixed concentrically with the inner ring 32 with respect to the peripheral surface 41 according to the amount of eccentricity of the annular inner peripheral surface 41. As a result, an engagement projection 53 is formed so as to protrude radially outward.
[0017]
Then, the engagement projection 53 is press-fitted to a position where the radial depth of the annular inner peripheral surface 41 is the deepest (a position where the eccentricity is the maximum), so that the cylindrical portion 52 is formed inside the annular shape of the mounting groove 40. The inner ring 32 is fitted and fixed to the peripheral surface 41 concentrically with the inner ring 32.
A relief portion 34 corresponding to the thickness of the annular portion 51 is formed at the end of the inner ring 32 adjacent to the mounting groove 40, and complements the annular portion 51 of the slinger 50 with the relief portion 34. The outer surface of the annular portion 51 can be made substantially flush with the end surface of the outer ring 31, and the axial width of the rolling bearing 30 including the slinger 50 can be reduced. In addition, since the clearance between the seal plate 35 and the annular portion 51 of the slinger 50 can be reduced, sufficient water resistance can be obtained.
[0018]
Further, the outer peripheral portion of the annular portion 51 of the slinger 50 of the present embodiment is bent inward in the axial direction and is disposed close to the seal plate 35, and the outer peripheral end of the annular portion 51 is formed of a sealing material of the seal plate 35. An annular projection 37a is provided on the inner peripheral surface of the annular projection 37a.
[0019]
When the rolling bearing 30 is used for an alternator or the like, the inner ring 32 is externally fitted and fixed to a rotating shaft (not shown) of the alternator, so that the lip portion of the seal plate 35 is formed by the annular portion 51 of the slinger 50. The sliding contact between the inner ring 32 and the inner ring 32 is prevented from directly splashing water, and the centrifugal force of the slinger 50 rotating together with the inner ring 32 blows off water adhering to the circular ring portion 51 of the slinger 50 to make the sliding contact. It is possible to prevent water or the like from entering the section.
[0020]
That is, according to the rolling bearing 30 according to the present embodiment, the cylindrical portion 52 of the slinger 50 is attached to the inner ring 32 with respect to the annular inner peripheral surface 41 of the mounting groove 40 formed on the inner peripheral surface of the end of the inner ring 32. An engagement protrusion 53 formed concentrically inside and fixed to the outer peripheral surface of the cylindrical portion 52 in accordance with the amount of eccentricity of the annular inner peripheral surface 41 eccentric with respect to the axis, It is pressed into the peripheral surface 41.
[0021]
Therefore, even when the rotating shaft rotates at a high speed, the cylindrical portion 52 of the slinger 50 does not deform in the radially expanding direction due to the centrifugal force. Since the slinger 50 is locked to the inner peripheral surface 41, the slinger 50 is prevented from rotating and is securely fixed.
Therefore, it is possible to provide the rolling bearing 30 that can be suitably used for an alternator of an automobile in which requirements for reliability are increased while conditions such as a wet environment are stricter in the future.
[0022]
FIG. 4 shows a conventional example in which the slinger 6 is combined with the conventional rolling bearing 10 shown in FIG. 5, and the rolling bearing 30 of the present embodiment shown in FIG. It shows the results of a comparative test of the amount of water penetration.
In addition, the said test made the specification (6202 size) of the rolling bearing other than a slinger the same, and performed it for 20 hours at the rotation speed 1500min- 1 and the water injection amount of 200cc / min (straight water of a slinger surface).
As is clear from FIG. 4, the rolling bearing 30 according to the present invention has no water infiltration into the bearing, and has significantly improved water resistance as compared with the conventional example in which the amount of water permeated is 100 mg.
[0023]
Note that the configuration of the inner and outer rings, rolling elements, seal members, slinger, mounting grooves, engagement protrusions, and the like in the rolling bearing of the present invention is not limited to the configuration of the above-described embodiment, but based on the gist of the present invention. It goes without saying that it can take various forms.
For example, although a ball bearing is used as a rolling bearing in the above embodiment, the present invention can be applied to other types of rolling bearings such as a roller bearing, and a non-contact type shield can be used as a seal member.
[0024]
【The invention's effect】
As described above, according to the above-described rolling bearing of the present invention, the cylindrical portion of the slinger is internally fitted and fixed concentrically with the inner ring with respect to the annular inner peripheral surface of the mounting groove formed on the inner peripheral surface at the end of the inner ring. At the same time, an engagement projection formed on the outer peripheral surface of the cylindrical portion according to the amount of eccentricity of the annular inner peripheral surface eccentric with respect to the axis is pressed into the annular inner peripheral surface.
Therefore, even when the rotating shaft rotates at a high speed, the cylindrical portion of the slinger does not deform in the radially expanding direction due to centrifugal force, and the engaging projection of the cylindrical portion engages with the eccentric inner peripheral surface of the mounting groove. Since the slinger is stopped, the slinger is prevented from rotating and is securely fixed.
Therefore, it is possible to provide a good rolling bearing that can obtain sufficient water resistance and can prevent the slinger from rotating together during high-speed rotation.
[Brief description of the drawings]
FIG. 1 is a sectional view of a main part of a rolling bearing according to an embodiment of the present invention.
FIG. 2 is an explanatory view of an arrangement of a cylindrical portion of a slinger with respect to an annular inner peripheral surface of a mounting groove shown in FIG. 1 as viewed from an axial end side.
FIG. 3 is a sectional view taken along line AA of FIG. 2;
FIG. 4 is a graph showing a comparison of the amount of water entering a rolling bearing between a conventional example and an example of the present invention.
FIG. 5 is a sectional view of a main part of a conventional rolling bearing.
FIG. 6 is a sectional view of a main part of another conventional rolling bearing.
[Explanation of symbols]
3 balls (rolling elements)
Reference Signs List 30 Rolling bearing 31 Outer ring 32 Inner ring 34 Relief section 40 Mounting groove 41 Annular inner peripheral surface 50 Slinger 51 Ring section 52 Cylindrical section 53 Engagement projection

Claims (3)

外輪と内輪との間に複数の転動体が周方向に転動可能に介装されると共に、軸線方向の少なくとも一方の端部開口がシール部材と伴にスリンガにより覆われる転がり軸受であって、
前記内輪の少なくとも一方の端部内周面に形成された取付溝が、軸線に対して偏心した円環状内周面を有すると共に、前記スリンガが、前記端部開口を覆う円輪部と、該円輪部の内周縁に形成された円筒部とを有しており、
前記取付溝の円環状内周面に対して前記内輪と同心に内嵌固定される前記円筒部の外周面には、該円環状内周面の偏心量に応じて係合突起が径方向外方に突出形成され、前記円環状内周面に圧入されることを特徴とする転がり軸受。A plurality of rolling elements are interposed between the outer ring and the inner ring so as to be able to roll in the circumferential direction, and at least one end opening in the axial direction is a rolling bearing covered with a slinger together with a seal member,
A mounting groove formed in at least one end inner peripheral surface of the inner ring has an annular inner peripheral surface eccentric to an axis, and the slinger covers the end opening; A cylindrical portion formed on the inner peripheral edge of the ring portion,
The outer peripheral surface of the cylindrical portion, which is fitted and fixed concentrically with the inner race with respect to the annular inner peripheral surface of the mounting groove, has an engagement projection on the outer periphery in the radial direction according to the amount of eccentricity of the annular inner peripheral surface. The rolling bearing is formed so as to protrude toward the inner side and is press-fitted into the annular inner peripheral surface. 前記円輪部の板厚に相当する逃げ部が、前記取付溝に隣接する内輪端部に形成されていることを特徴とする請求項１に記載の転がり軸受。The rolling bearing according to claim 1, wherein a relief portion corresponding to a plate thickness of the ring portion is formed at an end of the inner ring adjacent to the mounting groove. 前記内輪が、オルタネータの回転軸に外嵌固定されることを特徴とする請求項１又は２に記載の転がり軸受。The rolling bearing according to claim 1, wherein the inner ring is externally fitted and fixed to a rotating shaft of the alternator.
JP2002271665A 2002-09-18 2002-09-18 Roller bearing Withdrawn JP2004108487A (en)

Priority Applications (1)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106122284A (en) * 2015-05-04 2016-11-16 斯凯孚公司 Bearing including sealing flange
CN106122263A (en) * 2015-05-04 2016-11-16 斯凯孚公司 Bearing including resilient bearing flange
CN112762099A (en) * 2019-10-21 2021-05-07 通用汽车环球科技运作有限责任公司 Modular labyrinth bearing assembly

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106122284A (en) * 2015-05-04 2016-11-16 斯凯孚公司 Bearing including sealing flange
CN106122263A (en) * 2015-05-04 2016-11-16 斯凯孚公司 Bearing including resilient bearing flange
CN106122263B (en) * 2015-05-04 2019-12-17 斯凯孚公司 Bearing comprising an elastic bearing flange
CN106122284B (en) * 2015-05-04 2020-02-07 斯凯孚公司 Bearing comprising a sealing flange
CN112762099A (en) * 2019-10-21 2021-05-07 通用汽车环球科技运作有限责任公司 Modular labyrinth bearing assembly
CN112762099B (en) * 2019-10-21 2022-11-25 通用汽车环球科技运作有限责任公司 Modular labyrinth bearing assembly

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