JP2014088891A - Rolling bearing device - Google Patents

Rolling bearing device Download PDF

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JP2014088891A
JP2014088891A JP2012238130A JP2012238130A JP2014088891A JP 2014088891 A JP2014088891 A JP 2014088891A JP 2012238130 A JP2012238130 A JP 2012238130A JP 2012238130 A JP2012238130 A JP 2012238130A JP 2014088891 A JP2014088891 A JP 2014088891A
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Prior art keywords
outer ring
rolling
rolling bearing
bearing device
inner ring
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Japanese (ja)
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Osamu Higashimoto
修 東本
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JTEKT Corp
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • 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
    • 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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing device which can suppress uneven distribution of a lubricant inside the bearing and prevent failure of the bearing part due to poor lubrication.SOLUTION: A rolling bearing device 1 comprises: an outer ring 2 in whose inner periphery an outer ring raceway 2a is formed; an inner ring member 3 in whose outer periphery an inner ring raceway 3a is formed; a plurality of rolling elements 4 which roll between the outer ring raceway 2a and the inner ring raceway 3a; a retainer 5 which retains the plurality of rolling elements 4; and a sealing device 6 which is fitted into an inner periphery 2d at an axial end of the outer ring 2 and slidably contacts the inner ring member 3 to seal an internal space 10 between the inner periphery of the outer ring 2 and the outer periphery of the inner ring member 3. A lubricant 30 is enclosed in the internal space 10. The rolling bearing device 1 comprises: a shield 7 which is fixed to the inner ring 3 and arranged on the rolling element 4 side relative to the sealing device 6; and an oil receiving portion 2d which extends to the rolling element 4 side in an outer periphery of the shield 7.

Description

本発明は、密封装置を用いた転がり軸受装置に係り、より詳しくは、外輪回転で使用される転がり軸受装置に関する。   The present invention relates to a rolling bearing device using a sealing device, and more particularly to a rolling bearing device used in outer ring rotation.

従来、転がり軸受装置においては、軸受内部に封入したグリースなど潤滑剤の漏出の防止し、また、外部からの水や異物の進入防止のため、接触式または非接触式の密封装置が設けられている。例えば、接触式の密封装置として、外輪の両端開口部にシールケースを取り付け、そのシールケースの内側にシール部材を装着して、そのシールリップを内輪や軸などの軸部品に弾性的に接触させたものが知られている。   Conventionally, in a rolling bearing device, a contact type or non-contact type sealing device has been provided to prevent leakage of lubricant such as grease enclosed in the bearing and to prevent water and foreign matter from entering from the outside. Yes. For example, as a contact-type sealing device, a seal case is attached to both end openings of the outer ring, a seal member is attached to the inside of the seal case, and the seal lip is elastically brought into contact with a shaft component such as an inner ring or a shaft. Is known.

ところで、この種の密封装置は、外輪回転下で使用される転がり軸受装置、特に円すいころ軸受を備えた軸受装置にあっては所期の機能を十分に発揮できないとの問題を有する。すなわち、外輪回転下では、外輪回転に伴う遠心力で例えば軸受内部に充填された潤滑剤が軸受両端側に流動し易く、内輪回転の場合と比べて軸受内部の潤滑剤不足を招き易い。また、この種の密封装置は、通常、回転駆動する外輪に固定されるため、シールリップに遠心力が発生して内径側への押付け力が弱まる点もシール性を低下させる一因となっている。   By the way, this type of sealing device has a problem that a rolling bearing device used under rotation of the outer ring, particularly a bearing device provided with a tapered roller bearing, cannot sufficiently perform its intended function. That is, under the outer ring rotation, for example, the lubricant filled in the bearing easily flows to both ends of the bearing due to the centrifugal force accompanying the outer ring rotation, and the lubricant in the bearing is likely to be insufficient compared to the case of the inner ring rotation. In addition, since this type of sealing device is usually fixed to an outer ring that is rotationally driven, the point that centrifugal force is generated in the seal lip and the pressing force toward the inner diameter side is weakened also contributes to a decrease in sealing performance. Yes.

上記不具合を改善するための対策として、シールリップでシールされる空間内に非接触シールをさらに設け、この非接触シールのシールすき間を、シールリップと軸部品との摺接部よりも外径側に配置した、外輪回転型の転がり軸受装置が提案されている。（特許文献１参照）   As a measure to improve the above problems, a non-contact seal is further provided in the space sealed by the seal lip, and the seal clearance of the non-contact seal is set on the outer diameter side of the sliding contact portion between the seal lip and the shaft component. An outer ring rotation type rolling bearing device is proposed. (See Patent Document 1)

特開２０１１−５２７７５号公報JP 2011-52775 A

前述の特許文献１の転がり軸受装置において、シールリップと軸部品との摺接部からの潤滑剤の漏出は低減できる。しかしながら、回転する非接触シールに接触した潤滑剤は遠心力によって径方向外方に飛散し、軸方向転動体側へ導入されることはない。また、径方向外方に飛散した多量の潤滑剤が、シールの外輪との嵌合部の内周に滞留することは避けられない。   In the rolling bearing device disclosed in Patent Document 1, leakage of lubricant from the sliding contact portion between the seal lip and the shaft component can be reduced. However, the lubricant in contact with the rotating non-contact seal is scattered radially outward by centrifugal force and is not introduced to the axial rolling element side. Moreover, it is inevitable that a large amount of lubricant scattered radially outwards stays on the inner periphery of the fitting portion with the outer ring of the seal.

前記の滞留した多量の潤滑剤は、遠心力によって、外輪のシール嵌合部とシール外周の間を経由して、外部に漏出する危険がある。このため、特許文献１の転がり軸受装置において、潤滑剤の軸受内部での偏在を防止する効果は小さく、潤滑性能が大きく向上することはない。   There is a risk that a large amount of the retained lubricant leaks outside due to centrifugal force between the seal fitting portion of the outer ring and the outer periphery of the seal. For this reason, in the rolling bearing device of Patent Document 1, the effect of preventing uneven distribution of the lubricant inside the bearing is small, and the lubricating performance is not greatly improved.

本発明は、軸受内部の潤滑剤の偏在を抑制し、潤滑不良による軸受部の不具合を防止できる転がり軸受装置を提供することを目的としている。   An object of the present invention is to provide a rolling bearing device that suppresses uneven distribution of a lubricant inside a bearing and prevents a failure of a bearing portion due to poor lubrication.

上記の課題を解決するため、請求項１に係る発明の構成上の特徴は、内周に外輪軌道が形成された外輪と、外周に内輪軌道が形成された内輪部材と、前記外輪軌道と前記内輪軌道の間で転動する複数の転動体と、前記複数の転動体を保持する保持器と、前記外輪の軸方向端部の内周に嵌合され、前記内輪部材と摺接して前記外輪の内周と前記内輪部材の外周との間の内部空間を密封する密封装置と、を有し、前記内部空間に潤滑剤が封入された転がり軸受装置であって、前記内輪に固定され、前記密封装置に対し、前記転動体側に配置されたシールドを有し、前記シールドの外周に前記転動体側に延在する油受け部を有することである。   In order to solve the above-described problem, the structural features of the invention according to claim 1 include an outer ring having an outer ring raceway formed on an inner periphery, an inner ring member having an outer ring raceway formed on an outer periphery, the outer ring track, A plurality of rolling elements that roll between inner ring raceways, a cage that holds the plurality of rolling elements, and an inner periphery of an axial end of the outer ring, and are in sliding contact with the inner ring member and the outer ring And a sealing device that seals an inner space between the inner periphery of the inner ring member and the outer periphery of the inner ring member, and a rolling bearing device in which a lubricant is sealed in the inner space, and is fixed to the inner ring, The sealing device has a shield disposed on the rolling element side, and has an oil receiving portion extending on the rolling element side on the outer periphery of the shield.

本発明の構成によれば、転動体および保持器の回転によって径方向外方に飛散した潤滑剤は、軸方向に延在する前記シールドの油受け部に保持され、前記密封装置としてのシールの、前記外輪との嵌合部の内周に滞留する潤滑剤の量を、油受け部を有しない構成に対して軽減することができる。この結果、前記外輪のシールとの嵌合部と、前記シールの外輪との嵌合部の間を経由して、外部に漏出する潤滑油の量を軽減できる。また、前記油受け部に保持された潤滑剤は前記油受け部に沿って、前記転動体側に循環し、前記外輪軌道と前記内輪軌道と複数の転動体とで構成される軸受内部へ導入される。   According to the configuration of the present invention, the lubricant splashed radially outward by the rotation of the rolling elements and the cage is held in the oil receiving portion of the shield extending in the axial direction, and the seal as the sealing device Further, the amount of the lubricant staying on the inner periphery of the fitting portion with the outer ring can be reduced with respect to the configuration having no oil receiving portion. As a result, it is possible to reduce the amount of lubricating oil leaked to the outside through the gap between the fitting portion of the outer ring with the seal and the fitting portion of the seal with the outer ring. Further, the lubricant held in the oil receiving portion circulates along the oil receiving portion to the rolling element side, and is introduced into the bearing constituted by the outer ring raceway, the inner ring raceway, and a plurality of rolling elements. Is done.

上記の課題を解決するため、請求項２に係る発明の構成上の特徴は、前記油受け部の前記転動体側の先端部は、前記シールの前記外輪との嵌合部分における前記転動体側の端部より前記転動体側に位置していることである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 2 is that the tip of the oil receiving portion on the rolling element side is on the rolling element side in a fitting portion of the seal with the outer ring. It is located in the said rolling element side from the edge part.

本発明の構成によれば、前記油受け部の転動体側の先端部が前記シールの外輪との嵌合部の前記転動体方側の端部より前記転動体側に位置し、前記油受け部は、前記シールの外輪との嵌合部の内周を完全に覆うため、前記シールの外輪との嵌合部の内周に滞留する潤滑剤の量をさらに軽減し、軸受内部に留めることができる。さらに、滞留した潤滑剤が、外輪のシール嵌合部とシール外周の間を経由して、外部に漏出する危険を回避することができる。   According to the configuration of the present invention, the tip of the oil receiving portion on the rolling element side is positioned closer to the rolling element than the end on the rolling element side of the fitting portion with the outer ring of the seal, and the oil receiver The portion completely covers the inner circumference of the fitting portion with the outer ring of the seal, so that the amount of lubricant staying on the inner circumference of the fitting portion with the outer ring of the seal is further reduced and retained inside the bearing. Can do. Furthermore, it is possible to avoid the risk that the retained lubricant leaks outside through the space between the seal fitting portion of the outer ring and the outer periphery of the seal.

上記の課題を解決するため、請求項３に係る発明の構成上の特徴は、前記油受け部の前記転動体側の先端部と前記外輪の内周部との間で密封用微少隙間が形成されていることである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 3 is that a minute gap for sealing is formed between the tip of the oil receiving portion on the rolling element side and the inner peripheral portion of the outer ring. It has been done.

上記構成によれば、密封用微少隙間によって、前記油受け部の転動体側の先端部と前記外輪の内周部との間から流出する潤滑剤の量は大幅に減少する。この結果、前記シールの外輪との嵌合部の内周に滞留する潤滑剤の量がさらに軽減し、より多くの潤滑剤を軸受内部に留めることができる。   According to the above configuration, the amount of lubricant flowing out from between the front end portion of the oil receiving portion on the rolling element side and the inner peripheral portion of the outer ring is greatly reduced by the small sealing clearance. As a result, the amount of the lubricant staying in the inner periphery of the fitting portion with the outer ring of the seal is further reduced, and more lubricant can be retained inside the bearing.

上記の課題を解決するため、請求項４に係る発明の構成上の特徴は、前記油受け部の転動体側の先端にリップを有し、前記リップは前記外輪の内周に摺接することである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 4 is that the oil receiver has a lip at the tip of the rolling element side, and the lip is in sliding contact with the inner periphery of the outer ring. is there.

上記構成によれば、前記油受け部の転動体側の先端にリップと、前記外輪の内周との摺接によって、前記油受け部の転動体側の先端部と前記外輪の内周部との間からの潤滑油の流出を防止できる。前記シールの外輪との嵌合部の内周に滞留する潤滑剤の量をさらに軽減し、の潤滑剤を軸受内部に留めることができる。   According to the above configuration, the lip at the tip of the oil receiving portion on the rolling element side and the sliding contact between the inner periphery of the outer ring and the tip portion on the rolling element side of the oil receiving portion and the inner peripheral portion of the outer ring The lubricating oil can be prevented from flowing out from between the two. It is possible to further reduce the amount of the lubricant staying in the inner periphery of the fitting portion with the outer ring of the seal, and to keep the lubricant inside the bearing.

上記の課題を解決するため、請求項５に係る発明の構成上の特徴は、前記保持器は、軸方向前記密封装置側の端部が前記転動体の軸受外部側の端面より密封装置側に突出しており、前記シールドの前記転動体側の端部は、前記保持器の径方向外方側かつ密封装置側の端部より、径方向外方かつ転動体側に位置していることである。   In order to solve the above-described problem, the structural feature of the invention according to claim 5 is that the cage has an end on the sealing device side in the axial direction closer to the sealing device than an end surface on the bearing outer side of the rolling element. The end of the shield on the rolling element side of the shield is positioned radially outward and on the rolling element side from the radial outer side of the cage and the end on the sealing device side. .

転動体および保持器に付着した潤滑剤は、転動体および保持器の回転によって、保持器の径方向内側の面に沿って、シールド側に移動し、軸方向密封装置側の端部から保持器の径方向外方に飛散する。上記構成によれば、飛散した潤滑剤は、保持器の軸方向密封装置側の端部より軸方向転動体側に延在する前記前記シールドの油受け部に確実に保持される。   The lubricant adhering to the rolling elements and the cage moves to the shield side along the radial inner surface of the cage by the rotation of the rolling elements and the cage, and the cage from the end on the axial sealing device side. Spatters outward in the radial direction. According to the said structure, the scattered lubricant is reliably hold | maintained at the oil receiving part of the said shield extended from the edge part by the side of the axial direction sealing device of a holder | retainer to the axial direction rolling element side.

この結果、シールの外周部にあって外輪に嵌入される外輪嵌入部の内周に滞留する潤滑剤の量を大幅に軽減することができ、外輪のシール嵌合部とシール外周の間を経由して、外部に漏出する潤滑油の量をさらに軽減できる。また、前記油受け部に保持されたより多くの潤滑剤は前記油受け部に沿って、転動体側に循環し、軸受内部へ導入される。   As a result, the amount of lubricant remaining on the inner periphery of the outer ring insertion portion that is inserted into the outer ring in the outer periphery portion of the seal can be greatly reduced, and it passes between the seal fitting portion of the outer ring and the seal outer periphery. Thus, the amount of lubricating oil leaking to the outside can be further reduced. Further, more lubricant held in the oil receiving portion circulates along the oil receiving portion toward the rolling element and is introduced into the bearing.

上記の課題を解決するため、請求項６に係る発明の構成上の特徴は、前記シールドは、前記内輪に固定された部分から径方向外方に延在する円盤部を有し、前記円盤部から転動体側に形成された油受け部は、内周部の軸方向転動体側端部の直径が内周部の軸方向中央の直径より小さい形状に形成されていることである。   In order to solve the above-described problem, the structural feature of the invention according to claim 6 is that the shield has a disk part extending radially outward from a part fixed to the inner ring, and the disk part. The oil receiving part formed on the rolling element side from the inner side is formed in a shape in which the diameter of the axial direction rolling element side end part of the inner peripheral part is smaller than the diameter in the axial center of the inner peripheral part.

上記構成によれば、前記油受け部の内周は径方向が外方に凹形状となり、より多くの潤滑剤がより確実に、前記油受け部に保持される。   According to the above configuration, the inner circumference of the oil receiving portion is concave outward in the radial direction, and more lubricant is more reliably held in the oil receiving portion.

上記の課題を解決するため、請求項７に係る発明の構成上の特徴は、前記転がり軸受装置は前記内輪部材は静止し、前記外輪が回転することである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 7 is that the rolling bearing device is such that the inner ring member is stationary and the outer ring rotates.

上記構成によれば、前記シールドは、静止した内輪に固定されているため、回転するこがなく、前記油受け部に保持された潤滑剤は遠心力で径方向外方に飛散することが無く、前記シールの外輪との嵌合部の内周に滞留する潤滑剤の量はさらに軽減する。   According to the above configuration, since the shield is fixed to the stationary inner ring, the shield does not rotate, and the lubricant held in the oil receiving portion does not scatter radially outward due to centrifugal force. The amount of the lubricant staying on the inner periphery of the fitting portion with the outer ring of the seal is further reduced.

本発明によれば、軸受内部の潤滑剤の偏在を抑制し、潤滑不良による軸受部の不具合を防止できる転がり軸受装置を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the rolling bearing apparatus which suppresses the uneven distribution of the lubricant inside a bearing and can prevent the malfunction of the bearing part by poor lubrication can be provided.

本発明の第１の実施形態の転がり軸受装置の断面図である。It is sectional drawing of the rolling bearing apparatus of the 1st Embodiment of this invention. 図１の主要部の拡大図である。It is an enlarged view of the principal part of FIG. 本発明の第１の実施形態の転がり軸受装置の作用を説明する説明図である。It is explanatory drawing explaining an effect | action of the rolling bearing apparatus of the 1st Embodiment of this invention. 本発明の他の実施形態の転がり軸受装置の主要部の拡大断面図である。It is an expanded sectional view of the principal part of the rolling bearing apparatus of other embodiment of this invention.

この発明の実施の形態を、以下図面を参照して説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１は、本発明の第１の実施形態の転がり軸受装置の断面図である。
図２は図１の主要部の拡大図である。第１の実施形態の転がり軸受装置は軸方向に対称形状であるため、図２は一方の主要部のみを示している。 FIG. 1 is a sectional view of a rolling bearing device according to a first embodiment of the present invention.
FIG. 2 is an enlarged view of the main part of FIG. Since the rolling bearing device of the first embodiment is symmetrical in the axial direction, FIG. 2 shows only one main part.

図１および図２において、転がり軸受装置１は、内周部に２列の外輪軌道２ａが形成された外輪２と、外周部に内輪軌道３ａが形成された２個の内輪部材としての内輪３と、前記２列の外輪軌道２ａと前記２個の内輪３の内輪軌道３ａの間に転動自在に配置された２列の複数の転動体としての円すいころ４と、複数の円すいころ４を保持する２個の保持器５と、２個の密封装置としてのシール６と、２個のシールド７と、潤滑剤としてのグリース３０を有する。   1 and 2, a rolling bearing device 1 includes an outer ring 2 in which two rows of outer ring raceways 2a are formed on the inner peripheral portion, and an inner ring 3 as two inner ring members in which inner ring raceways 3a are formed on the outer peripheral portion. A plurality of tapered rollers 4 as a plurality of rolling elements arranged in a freely rolling manner between the two rows of outer ring raceways 2 a and the inner ring raceways 3 a of the two inner rings 3, and a plurality of tapered rollers 4. Two retainers 5 to be held, two seals 6 as sealing devices, two shields 7, and grease 30 as a lubricant are provided.

外輪２は軸受鋼等の鋼材からなる環体で、内周の軸方向中央部には２列の円すい形状の外輪軌道２ａが軸方向外方を大径として形成されている。２列の外輪軌道２ａの大径側端部から径方向外方にそれぞれ軌道端面２ｃが形成され、両側の軌道端面２ｃの径方向外方縁部から軸方向外方にそれぞれ外輪側面２ｂまで、２列の円筒形状のシール嵌合面２ｄが延在する。   The outer ring 2 is an annular body made of a steel material such as bearing steel, and two rows of conical outer ring raceways 2a are formed in the axially central portion of the inner circumference with the outer diameter in the axial direction being a large diameter. Track end surfaces 2c are formed radially outward from the large-diameter side ends of the two rows of outer ring raceways 2a, respectively, and radially outer edges of both track end surfaces 2c are axially outward from the outer ring side surfaces 2b, respectively. Two rows of cylindrical seal fitting surfaces 2d extend.

２個の内輪３は軸受鋼等の鋼材からなる環体で、外周軸方向中央部に円すい形の内輪軌道３ａ、内輪軌道３ａの大径側端部から一方側端部に拡径して大鍔３ｃ、内輪軌道３ａの小径側端部から他方側端部に小鍔３ｆが形成されている。大鍔３ｃにおいて、内輪軌道３ａの大径側端部から内輪軌道３ａ方向に傾斜する大鍔面３ｄが径方向外方の大鍔外周面３ｅまで延在する。大鍔外周面３ｅは円筒形状で、大鍔面３ｄと反対側の端部は径方向内方に延在する大鍔側面３ｂに連なっている。   The two inner rings 3 are ring bodies made of a steel material such as bearing steel. The inner ring raceway 3a has a conical inner ring raceway 3a at the center in the outer peripheral axial direction, and the diameter of the inner ring raceway 3a is increased from the large-diameter end to the one end. A small flange 3f is formed from the small diameter side end of the flange 3c and the inner ring raceway 3a to the other end. In the large collar 3c, a large collar surface 3d that inclines in the direction of the inner ring raceway 3a from the end portion on the large diameter side of the inner ring raceway 3a extends to the outer circumference surface 3e of the large collar. The outer peripheral surface 3e of the large bowl is cylindrical, and the end opposite to the large bowl surface 3d is continuous with the large bowl side surface 3b extending radially inward.

保持器５は炭素鋼板等の鋼材からなり、プレス加工によって環体に形成されている。軸方向一方の端部に大円環部５ａ、他方の端部に小円環部５ｂ、大円環部５ａと小円環部５ｂを軸方向に連結する複数の柱部５ｃを有する。大円環部５ａと小円環部５ｂと２個の柱部５ｃとで複数の円すいころ４を保持する複数のポケット５ｄが円周上等配に区画形成されている。   The cage 5 is made of a steel material such as a carbon steel plate, and is formed into an annular body by pressing. The large annular portion 5a is provided at one end portion in the axial direction, the small annular portion 5b is provided at the other end portion, and a plurality of column portions 5c that connect the large annular portion 5a and the small annular portion 5b in the axial direction. A plurality of pockets 5d for holding a plurality of tapered rollers 4 are partitioned and formed equally on the circumference by the large ring portion 5a, the small ring portion 5b, and the two column portions 5c.

円すいころ４は軸受鋼等の鋼材からなり、円すい形状の転動面４ａ、大端面４ｂ、小端面４ｃを有する。２列の複数の円すいころ４は２個の保持器５の複数のポケット５ｄ内にそれぞれ保持され、大端面４ｂを内輪３の大鍔面３ｄに接し、転動面４ａを外輪軌道２ａと内輪軌道３ａに接して、転動自在に配置され、外輪軌道２ａと内輪軌道３ａとともに軸受部２０を構成している。また、保持器５の大円環部５ａは円すいころ４の大端面４ｂより軸受外方側に突出している。   The tapered roller 4 is made of a steel material such as bearing steel and has a tapered rolling surface 4a, a large end surface 4b, and a small end surface 4c. Two rows of tapered rollers 4 are respectively held in a plurality of pockets 5d of two cages 5, the large end surface 4b is in contact with the large collar surface 3d of the inner ring 3, and the rolling surface 4a is connected to the outer ring raceway 2a and the inner ring. In contact with the raceway 3a, the bearing portion 20 is arranged together with the outer raceway 2a and the inner raceway 3a. Further, the large annular portion 5 a of the cage 5 protrudes outward from the large end surface 4 b of the tapered roller 4.

シール６は、炭素鋼板等の鋼材をプレス加工により円環状に形成された芯金６ａと、合成ゴム等の弾性体からなるシールリップ６ｂとで構成されている。芯金６ａは円盤部６ｃと円盤部６ｃの外周から軸方向に延在する円筒部６ｄからなり、円盤部６ｃの内周部にシールリップ６ｂが先端を軸方向円筒部側に向けて加硫接着されている。２個のシール６はそれぞれ円筒部６ｄが外輪２のシール嵌合面２ｄに嵌入固定され、シールリップ６ｂの先端が内輪３の大鍔側面３ｂに摺接して、外輪２の内周と２個の内輪３の外周との間の内部空間１０を密封している。また、内部空間１０には潤滑剤としてのグリース３０が封入されている。   The seal 6 includes a cored bar 6a formed in an annular shape by pressing a steel material such as a carbon steel plate, and a seal lip 6b made of an elastic body such as synthetic rubber. The cored bar 6a is composed of a disk part 6c and a cylindrical part 6d extending in the axial direction from the outer periphery of the disk part 6c, and a seal lip 6b is vulcanized on the inner peripheral part of the disk part 6c with the tip directed toward the axial cylindrical part. It is glued. The two seals 6 each have a cylindrical portion 6 d fitted and fixed to the seal fitting surface 2 d of the outer ring 2, the tip of the seal lip 6 b is in sliding contact with the large collar side surface 3 b of the inner ring 3, and the inner circumference of the outer ring 2 and the two seals 6. The inner space 10 between the inner ring 3 and the outer periphery of the inner ring 3 is sealed. The internal space 10 is filled with grease 30 as a lubricant.

シールド７は炭素鋼板等の鋼材からなり、プレス加工によって、断面形状がコの字型の円環状に形成されている。シールド７は円盤状の側板部７ｂの外周一方側に油受け部としての円筒形の第１円筒部７ａが形成され、側板部７ｂの内周には軸方向第１円筒部７ａと同一方向に第２円筒部７ｃが形成されている。第１円筒部７ａの側板部７ｂと反対側の端部には径方向内方に外輪軌道２と略同じ傾斜角で傾斜した傾斜部７ｆを有している。   The shield 7 is made of a steel material such as a carbon steel plate, and is formed in an annular shape with a U-shaped cross-section by pressing. The shield 7 is formed with a cylindrical first cylindrical portion 7a as an oil receiving portion on one side of the outer periphery of the disc-shaped side plate portion 7b, and the inner periphery of the side plate portion 7b is in the same direction as the axial first cylindrical portion 7a. A second cylindrical portion 7c is formed. An end portion of the first cylindrical portion 7a opposite to the side plate portion 7b has an inclined portion 7f inclined inward in the radial direction at substantially the same inclination angle as the outer ring raceway 2.

第１円筒部７ａの外径寸法、および第１円筒部７ａの側板部７ｂから傾斜部７ｆの先端までの軸方向の長さは、シールド７を大鍔外周面３ｅの所定の位置に嵌入した時、傾斜部７ｆの外周と外輪軌道２ａとの間に密封用微少隙間Δが形成できる寸法となっている。   The outer diameter dimension of the first cylindrical portion 7a and the axial length from the side plate portion 7b of the first cylindrical portion 7a to the tip of the inclined portion 7f are inserted into the shield 7 at a predetermined position on the outer peripheral surface 3e. At this time, the dimension is such that a small sealing clearance Δ can be formed between the outer periphery of the inclined portion 7f and the outer ring raceway 2a.

２個のシールド７は、それぞれ、側板部７ｂを内輪３の大鍔側面３ｂ側に向け、第２円筒部７ｃを２個の内輪３の大鍔外周面３ｅの所定の位置に嵌入され、２個の内輪３に固定されている。この時、シールド７の傾斜部７ｆの外周と外輪軌道２ａとの間に前述の密封用微少隙間Δが形成されている。また、シールド７の傾斜部７ｆを含む第１円筒部７ａの内周面は保持器５の大円環部部５ｃの径方向外方に位置し、油受け面７ｅとなっている。   Each of the two shields 7 is fitted into a predetermined position on the outer peripheral surface 3e of the large inner surface 3e of the two inner rings 3 with the side plate portion 7b facing the large inner surface 3b side of the inner ring 3 and the second cylindrical portion 7c. It is fixed to the individual inner ring 3. At this time, the above-described minute gap Δ for sealing is formed between the outer periphery of the inclined portion 7f of the shield 7 and the outer ring raceway 2a. Further, the inner peripheral surface of the first cylindrical portion 7a including the inclined portion 7f of the shield 7 is located radially outward of the great annular portion 5c of the cage 5, and serves as an oil receiving surface 7e.

シールド７の第１円筒部７ａの内周面と保持器５の大円環部部５ｃの径方向外方の端部の間、シールド７の側板部７ｂと保持器５の大円環部部５ｃの軸方向シールド７側の端部の間、および、シールド７の側板部７ｂとシール６の円盤部６ｃの間にはそれぞれ隙間を有している。   Between the inner peripheral surface of the first cylindrical portion 7a of the shield 7 and the radially outer end of the large annular portion 5c of the cage 5, the side plate portion 7b of the shield 7 and the large annular portion of the cage 5 There are gaps between the end portions on the axial shield 7 side of 5 c and between the side plate portion 7 b of the shield 7 and the disk portion 6 c of the seal 6.

以下、転がり軸受装置１の組立工程の例を説明する。２列の複数の円すいころ４と、複数の円すいころ４を保持する２個の保持器５が組み込まれた２個の内輪３が外輪２に軸方向両側から組み込まれる。この状態で軸方向両側の開放部から外輪２の内周と２個の内輪３の外周との間の軸受部２０を含む内部空間１０にグリース３０が注入さる。   Hereinafter, an example of an assembly process of the rolling bearing device 1 will be described. Two inner rings 3 in which two rows of tapered rollers 4 and two cages 5 holding the plurality of tapered rollers 4 are incorporated are incorporated into the outer ring 2 from both sides in the axial direction. In this state, the grease 30 is injected into the internal space 10 including the bearing portion 20 between the inner periphery of the outer ring 2 and the outer periphery of the two inner rings 3 from the open portions on both axial sides.

次に軸方向両側の開放部から、２個のシールド７が、側板部７ｂを軸受外方に向け。第２円筒部７ｃが２個の内輪３の大鍔外周面３ｅに外嵌して、所定の位置に嵌入される。この後、２個のシール６はそれぞれシールリップ６ｂの先端が内輪３の大鍔側面３ｂに摺接して、円筒部６ｄが外輪２のシール嵌合面２ｄに嵌入固定され、組立は完了する。   Next, two shields 7 face the side plate portion 7b outward from the open portions on both axial sides. The second cylindrical portion 7c is fitted on the outer circumference 3e of the two inner rings 3 and is inserted into a predetermined position. Thereafter, the ends of the seal lips 6b of the two seals 6 are brought into sliding contact with the large flange side surface 3b of the inner ring 3, and the cylindrical portion 6d is fitted and fixed to the seal fitting surface 2d of the outer ring 2, thereby completing the assembly.

図３は本発明の第１の実施形態の転がり軸受装置の作用を説明する説明図である。
第１の実施形態の転がり軸受装置１は前述の組立完了の時点で、グリース３０が２個のシールド７によって軸受部２０に押し込まれ、軸受部２０の潤滑条件はシールド７を有しない場合にくらべ大きく改善されている。 FIG. 3 is an explanatory view for explaining the operation of the rolling bearing device according to the first embodiment of the present invention.
In the rolling bearing device 1 according to the first embodiment, the grease 30 is pushed into the bearing portion 20 by the two shields 7 at the time of the completion of the assembly, and the lubrication condition of the bearing portion 20 is compared with the case where the shield 7 is not provided. Greatly improved.

以下、図３によって第１の実施形態の転がり軸受装置１の作用を説明する。以下の説明において、転がり軸受装置１は、内輪３が静止し、外輪２が回転するものとする。白抜き矢印はグリース３０の流れを模式的に示している。
外輪２の回転によって、複数のころ４は自転とともに公転し、複数のころ４を保持する保持器５も回転する。複数のころ４の公転、保持器５の回転によって軸受部２０に封入されたグリース３０も回転し、グリース３０の自重によってグリース３０に遠心力が作用する。 Hereinafter, the operation of the rolling bearing device 1 of the first embodiment will be described with reference to FIG. In the following description, in the rolling bearing device 1, it is assumed that the inner ring 3 is stationary and the outer ring 2 is rotated. The white arrow schematically shows the flow of the grease 30.
The rotation of the outer ring 2 causes the plurality of rollers 4 to revolve together with rotation, and the cage 5 that holds the plurality of rollers 4 also rotates. The grease 30 enclosed in the bearing portion 20 is also rotated by the revolution of the plurality of rollers 4 and the rotation of the cage 5, and centrifugal force acts on the grease 30 due to its own weight.

軸受部２０において、保持器５の径方向内方に位置するグリース３０は前記遠心力によって保持器５の大円環部５ａ及び柱部５ｃの内周面に押付けられ、前記内周面の傾斜に沿って大円環部５ａのシールド７側の端部側に移動し、前記端部から径方向外方に飛散する。飛散したグリース３０はシールド７の油受け面７ｅに受け止められ、油受け面７ｅに滞留する。シールド７は静止しているため、油受け面７ｅに滞留したグリース３０はその自重で重力方向に移動し、鍔外周面３ｅを経由して軸受部２０に戻される。   In the bearing portion 20, the grease 30 positioned radially inward of the cage 5 is pressed against the inner circumferential surfaces of the large annular portion 5 a and the column portion 5 c of the cage 5 by the centrifugal force, and the inner circumferential surface is inclined. And moves toward the end of the great ring portion 5a on the shield 7 side, and scatters radially outward from the end. The scattered grease 30 is received by the oil receiving surface 7e of the shield 7 and stays on the oil receiving surface 7e. Since the shield 7 is stationary, the grease 30 staying on the oil receiving surface 7e moves in the gravitational direction by its own weight and is returned to the bearing portion 20 via the outer peripheral surface 3e.

保持器５の径方向外方に位置するグリース３０のうち大部分は前記遠心力によって外輪軌道２ａに押付けられ、外輪軌道２ａの傾斜に沿って外輪軌道２ａの大径側に移動する。大径側に移動したグリース３０は、シールド７の傾斜部７ｆに達するが、外輪軌道２ａとシールド７の傾斜部７ｆの外周と外輪軌道２ａとの間には密封用微少隙間Δが形成されており、多くのグリース３０が密封用微少隙間Δを経由してシール６の円筒部６ｄに達することは無い。   Most of the grease 30 positioned radially outward of the cage 5 is pressed against the outer ring raceway 2a by the centrifugal force, and moves to the larger diameter side of the outer ring raceway 2a along the inclination of the outer ring raceway 2a. The grease 30 moved to the large diameter side reaches the inclined portion 7f of the shield 7, but a small sealing clearance Δ is formed between the outer ring raceway 2a and the outer periphery of the inclined portion 7f of the shield 7 and the outer ring raceway 2a. Thus, a large amount of grease 30 does not reach the cylindrical portion 6d of the seal 6 via the minute sealing gap Δ.

大部分のシールド７の傾斜部７ｆに達したグリース３０はシールド７の傾斜部７ｆを経由して油受け面７ｅに滞留する。また、保持器５の径方向外方に位置するグリース３０のうち一部分は前記遠心力によって、直接シールド７の油受け面７ｅに受け止められ、油受け面７ｅに滞留する。油受け面７ｅに滞留したグリース３０はその自重で重力方向に移動し、鍔外周面３ｅを経由して軸受部２０に戻される。   Most of the grease 30 reaching the inclined portion 7f of the shield 7 stays on the oil receiving surface 7e via the inclined portion 7f of the shield 7. Further, a part of the grease 30 positioned radially outward of the cage 5 is directly received by the oil receiving surface 7e of the shield 7 by the centrifugal force and stays on the oil receiving surface 7e. The grease 30 staying on the oil receiving surface 7e moves in the direction of gravity by its own weight, and is returned to the bearing portion 20 via the outer peripheral surface 3e.

このように、シール６の円筒部６ｄ内周に滞留するグリース３０の量を、シールド７の油受け面７ｅを有しない構成に対して大幅軽減することができ、外輪２のシール嵌合部２ｄと、シール６の円筒部６ｄの外周との間を経由して、外部に漏出するグリースの量を軽減できる。また、油受け面７ｅに保持されたグリース３０はシールド７に沿って循環し、軸受内部１０へ導入される。   In this way, the amount of grease 30 staying on the inner periphery of the cylindrical portion 6d of the seal 6 can be greatly reduced compared to the configuration without the oil receiving surface 7e of the shield 7, and the seal fitting portion 2d of the outer ring 2 can be reduced. And the amount of grease leaking to the outside via the space between the outer periphery of the cylindrical portion 6d of the seal 6 can be reduced. Further, the grease 30 held on the oil receiving surface 7 e circulates along the shield 7 and is introduced into the bearing interior 10.

外輪が固定され、内輪が回転する場合は、シールド７の回転により、油受け面７ｅに滞留したグリース３０が回転中に鍔外周面３ｅを経由して軸受部２０に戻される効果は認められないが、停止期間においては、油受け面７ｅに滞留したグリース３０が鍔外周面３ｅを経由して軸受部２０に戻される。また、外輪が回転する場合と同様、外輪軌道２ａの大径側に移動したグリース３０が密封用微少隙間Δを経由してシール６の円筒部６ｄに達することは無い。   When the outer ring is fixed and the inner ring rotates, the effect that the grease 30 staying on the oil receiving surface 7e is returned to the bearing portion 20 through the outer peripheral surface 3e during rotation by the rotation of the shield 7 is not recognized. However, during the stop period, the grease 30 staying on the oil receiving surface 7e is returned to the bearing portion 20 through the outer peripheral surface 3e. Similarly to the case where the outer ring rotates, the grease 30 that has moved to the larger diameter side of the outer ring raceway 2a does not reach the cylindrical portion 6d of the seal 6 via the small sealing gap Δ.

このように、第１の実施形態の転がり軸受装置１はシール６の円筒部６ｄの内周に滞留するグリース３０の量を軽減し、外部に漏出するグリース３０の量を軽減できる。また、油受け面７ｅに保持されたグリース３０は軸受内部へ導入され、内部空間１０のグリースの偏在を抑制し、潤滑不良による転がり軸受装置の不具合を防止できる。   As described above, the rolling bearing device 1 according to the first embodiment can reduce the amount of the grease 30 staying on the inner periphery of the cylindrical portion 6d of the seal 6 and can reduce the amount of the grease 30 leaking to the outside. Further, the grease 30 held on the oil receiving surface 7e is introduced into the bearing, thereby suppressing the uneven distribution of the grease in the internal space 10 and preventing the rolling bearing device from malfunctioning due to poor lubrication.

上述の第１の実施形態の転がり軸受装置１では、第１円筒部７ａの先端と外輪軌道２ａとの間で微少隙間Δが形成されているが、この発明では、図４に示す様に、油受け部としての第１円筒部１７ａの先端に外輪軌道２ａに摺接するリップ１７ｇを有する構成の転がり軸受装置１１であっても良い。   In the rolling bearing device 1 of the first embodiment described above, a minute gap Δ is formed between the tip of the first cylindrical portion 7a and the outer ring raceway 2a. In the present invention, as shown in FIG. The rolling bearing device 11 may be configured to have a lip 17g slidably contacting the outer ring raceway 2a at the tip of the first cylindrical portion 17a as an oil receiving portion.

上述の実施形態では、油受け部としての第１円筒部７ａは円筒形であるが、この発明では、油受け部は球状等他の形状であっても良い。   In the above-described embodiment, the first cylindrical portion 7a as the oil receiving portion has a cylindrical shape. However, in the present invention, the oil receiving portion may have another shape such as a spherical shape.

上述の実施形態では、シールド７の油受け部としての第１円筒部７ａの軸方向転動体側の端部の位置は外輪軌道２ａの径方向内方であるが、この発明では、第１円筒部７ａの軸方向転動体側の端部の位置は、軸受の形式等により、可能な限り転動体に近い位置であればよい。   In the above-described embodiment, the position of the end portion on the axial rolling element side of the first cylindrical portion 7a as the oil receiving portion of the shield 7 is inward in the radial direction of the outer ring raceway 2a. The position of the end of the portion 7a on the axial rolling element side may be a position as close to the rolling element as possible depending on the type of the bearing.

上述の実施形態では、潤滑剤はグリースであるが、この発明では、潤滑剤は高粘度潤滑油等グリース以外の液状潤滑剤であっても良い。   In the above-described embodiment, the lubricant is grease. However, in the present invention, the lubricant may be a liquid lubricant other than grease such as high viscosity lubricating oil.

上述の実施形態では、転動体は２列の複数の円すいころであるが、この発明では、転動体は単列の複数の円筒ころ等、他の列数や形式の転動体であっても良い。   In the above-described embodiment, the rolling elements are a plurality of tapered rollers in two rows. However, in this invention, the rolling elements may be rolling elements of other numbers or types such as a plurality of cylindrical rollers in a single row. .

１、１１ ‥ 転がり軸受装置
２ ‥ 外輪
２ａ ‥ 外輪軌道
３ ‥ 内輪（内輪部材）
３ａ ‥ 内輪軌道
４ ‥ 円すいころ（転動体）
５ ‥ 保持器
６ ‥ シール（密封装置）
７、１７ ‥ シールド
７ａ、１７ａ‥ 第１円筒部（油受け部）
７ｂ、１７ｂ‥ 円盤部
７ｅ、１７ｅ‥ 油受け面
１７ｇ ‥ リップ
１０ ‥ 内部空間
２０ ‥ 軸受部
３０ ‥ グリース（潤滑剤）
Δ ‥ 密封用微少隙間 1, 11 ... Rolling bearing device 2 ... Outer ring 2a ... Outer ring raceway 3 ... Inner ring (inner ring member)
3a ... Inner ring raceway 4 ... Tapered rollers (rolling elements)
5 ... Cage 6 ... Seal (sealing device)
7, 17 ... Shield 7a, 17a ... 1st cylindrical part (oil receiving part)
7b, 17b ... Disc part 7e, 17e ... Oil receiving surface 17g ... Lip 10 ... Internal space 20 ... Bearing part 30 ... Grease (lubricant)
Δ ・ ・ ・ Small gap for sealing

Claims (7)

内周に外輪軌道が形成された外輪と、外周に内輪軌道が形成された内輪部材と、前記外輪軌道と前記内輪軌道の間で転動する複数の転動体と、前記複数の転動体を保持する保持器と、前記外輪の軸方向端部の内周に嵌合され、前記内輪部材と摺接して前記外輪の内周と前記内輪部材の外周との間の内部空間を密封する密封装置と、を有し、前記内部空間に潤滑剤が封入された転がり軸受装置であって、
前記内輪に固定され、前記密封装置に対し、前記転動体側に配置されたシールドを有し、前記シールドの外周に前記転動体側に延在する油受け部を有することを特徴とする転がり軸受装置。 An outer ring having an outer ring raceway formed on the inner periphery, an inner ring member having an inner ring raceway formed on the outer periphery, a plurality of rolling elements that roll between the outer ring raceway and the inner ring raceway, and the plurality of rolling elements are retained. And a sealing device that is fitted to the inner periphery of the axial end portion of the outer ring and seals the inner space between the inner periphery of the outer ring and the outer periphery of the inner ring member in sliding contact with the inner ring member. A rolling bearing device in which a lubricant is sealed in the internal space,
A rolling bearing having a shield fixed to the inner ring and disposed on the rolling element side with respect to the sealing device, and having an oil receiving portion extending on the rolling element side on an outer periphery of the shield. apparatus. 前記油受け部の前記転動体側の先端部は、前記密封装置の前記外輪との嵌入部分における前記転動体方側の端部より前記転動体側に位置していることを特徴とする請求項１に記載の転がり軸受装置。   The tip of the oil receiving portion on the rolling element side is located closer to the rolling element than an end on the rolling element side in a fitting portion of the sealing device with the outer ring. The rolling bearing device according to 1. 前記油受け部の先端部と前記外輪の内周部との間で密封用微少隙間が形成されていることを特徴とする請求項１または請求項２に記載の転がり軸受装置。   The rolling bearing device according to claim 1, wherein a minute gap for sealing is formed between a tip end portion of the oil receiving portion and an inner peripheral portion of the outer ring. 前記油受け部の先端にリップを有し、前記リップは前記外輪の内周に摺接することを特徴とする請求項１または請求項２に記載の転がり軸受装置。   The rolling bearing device according to claim 1, wherein a lip is provided at a tip of the oil receiving portion, and the lip is in sliding contact with an inner periphery of the outer ring. 前記保持器は、軸方向前記密封装置側の端部が前記転動体の軸受外部側の端面より前記密封装置側に突出しており、前記シールドの径方向内方側かつ前記転動体側の端部は、前記保持器の前記密封装置側の端部より、径方向外方かつ前記転動体側に位置していることを特徴と請求項１に記載の転がり軸受装置。   In the cage, an end portion on the sealing device side in the axial direction protrudes from the end surface on the bearing outer side of the rolling element toward the sealing device side, and the end portion on the radially inner side of the shield and the rolling element side The rolling bearing device according to claim 1, wherein the rolling bearing device is located radially outward from the end of the cage on the sealing device side and on the rolling element side. 前記シールドは、前記内輪に固定された部分から径方向外方に延在する円盤部を有し、前記油受け部は前記円盤部から前記転動体側に延在する円筒形に形成されていることを特徴とする請求項１から請求項５のいずれか一項に記載の転がり軸受装置。   The shield has a disk part extending radially outward from a portion fixed to the inner ring, and the oil receiving part is formed in a cylindrical shape extending from the disk part to the rolling element side. The rolling bearing device according to any one of claims 1 to 5, wherein the rolling bearing device is provided. 前記転がり軸受装置は前記内輪部材は静止し、前記外輪が回転することを特徴とする請求項１から請求項６のいずれか一項に記載の転がり軸受装置。   The rolling bearing device according to any one of claims 1 to 6, wherein the inner ring member is stationary and the outer ring rotates in the rolling bearing device.
JP2012238130A 2012-10-29 2012-10-29 Rolling bearing device Pending JP2014088891A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10619674B1 (en) * 2019-01-14 2020-04-14 Aktiebolaget Skf Bearing assembly
JP2021001630A (en) * 2019-06-20 2021-01-07 内山工業株式会社 Seal structure
CN112780689A (en) * 2019-11-11 2021-05-11 斯凯孚公司 Rolling element bearing assembly
CN112780690A (en) * 2019-11-11 2021-05-11 斯凯孚公司 Rolling element bearing assembly
US11384793B2 (en) * 2018-06-29 2022-07-12 Schaeffler Technologies AG & Co. KG Rolling bearings having an integrated current-removal function

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11384793B2 (en) * 2018-06-29 2022-07-12 Schaeffler Technologies AG & Co. KG Rolling bearings having an integrated current-removal function
US10619674B1 (en) * 2019-01-14 2020-04-14 Aktiebolaget Skf Bearing assembly
CN111434937A (en) * 2019-01-14 2020-07-21 斯凯孚公司 Bearing assembly
CN111434937B (en) * 2019-01-14 2024-04-05 斯凯孚公司 Bearing assembly
JP2021001630A (en) * 2019-06-20 2021-01-07 内山工業株式会社 Seal structure
JP7323890B2 (en) 2019-06-20 2023-08-09 内山工業株式会社 Sealed structure
CN112780689A (en) * 2019-11-11 2021-05-11 斯凯孚公司 Rolling element bearing assembly
CN112780690A (en) * 2019-11-11 2021-05-11 斯凯孚公司 Rolling element bearing assembly
US11428269B2 (en) * 2019-11-11 2022-08-30 Aktiebolaget Skf Rolling-element bearing assembly
US11655854B2 (en) * 2019-11-11 2023-05-23 Aktiebolaget Skf Rolling-element bearing assembly

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