JP2008267431A - Double row tapered roller bearing device - Google Patents

Double row tapered roller bearing device Download PDF

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Publication number
JP2008267431A
JP2008267431A JP2007108361A JP2007108361A JP2008267431A JP 2008267431 A JP2008267431 A JP 2008267431A JP 2007108361 A JP2007108361 A JP 2007108361A JP 2007108361 A JP2007108361 A JP 2007108361A JP 2008267431 A JP2008267431 A JP 2008267431A
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Prior art keywords
tapered roller
inner ring
row
roller bearing
row tapered
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JP2007108361A
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Japanese (ja)
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Yukihiro Kataoka
幸浩 片岡
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2007108361A priority Critical patent/JP2008267431A/en
Publication of JP2008267431A publication Critical patent/JP2008267431A/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
    • F16C33/7803—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
    • 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
    • F16C2326/10—Railway vehicles

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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

<P>PROBLEM TO BE SOLVED: To prevent a front lid or a back lid from being easily separated from a bearing main body. <P>SOLUTION: A double row tapered roller bearing 20 comprises a pair of inner rings 22 having a raceway track on the outer periphery respectively, an outer ring 24 having double row raceway track on the inner periphery, a double row tapered roller 26 interposed between the raceway track of the inner ring 22 and the raceway track of the outer ring 24, a retainer 28 to retain the tapered roller 26 of each row, annular members 42, 44 positioned on both axial sides of a pair of the inner rings 22, and a sealing unit 30 disposed on both ends of the outer ring 24. The inner ring 22 and the annular members 42, 44 are spaced with clearances δa, δin the axial and radial directions by fitting a projection in a depression. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は複列円すいころ軸受装置に関し、鉄道車両車軸用軸受装置などに利用することができる。   The present invention relates to a double row tapered roller bearing device, and can be used for a bearing device for a railway vehicle axle.

密封型の鉄道車両車軸用軸受は、内部に充填したグリースその他の潤滑剤の洩れを防止し、また、水や塵埃など異物が侵入するのを防止するため、密封装置を用いている。密封装置は、図５に示すように、オイルシール８を保持した金属製のシールケース６を軸受２の外輪４の両端開口部に圧入することによって構成されている。オイルシール８のシールリップはメインリップ１０とダストリップ１２とからなり、これらは車軸と共に回転する環状部材１６たとえば前蓋や後蓋の外周面に弾性的に密着する。言い換えれば、環状部材１６の外周面１８がシールリップ１０，１２のためのシールランドを提供する。そして、一般に、メインリップ１０にガータースプリング１４で適度な緊迫力を与えることで、軸受２と環状部材１６の分離を抑制するようにしている（特許文献１参照）。   Sealed railway vehicle axle bearings use a sealing device to prevent leakage of grease and other lubricants filled therein, and to prevent foreign substances such as water and dust from entering. As shown in FIG. 5, the sealing device is configured by press-fitting a metal seal case 6 holding an oil seal 8 into both end openings of the outer ring 4 of the bearing 2. The seal lip of the oil seal 8 is composed of a main lip 10 and a dust lip 12, which are elastically adhered to an outer peripheral surface of an annular member 16 that rotates with the axle, for example, a front lid or a rear lid. In other words, the outer peripheral surface 18 of the annular member 16 provides a seal land for the seal lips 10, 12. In general, the main lip 10 is restrained from being separated from the bearing 2 and the annular member 16 by applying an appropriate tightening force by the garter spring 14 (see Patent Document 1).

なお、特許文献２，３にはフレッティング摩耗対策として、前蓋と内輪との間および後蓋と内輪との間に黄銅板を挟む技術が記載されている。
特開２００６−１７０３２５号公報 特開２００３−４９８５６号公報 特開２００４−３３２９０５号公報 Patent Documents 2 and 3 describe techniques for sandwiching a brass plate between the front lid and the inner ring and between the rear lid and the inner ring as countermeasures against fretting wear.
JP 2006-170325 A JP 2003-49856 A JP 2004-332905 A

近時、鉄道車両の高速化が進むにつれ、シールの密封性を保ちつつ軸受の発熱低減のため、シールリップとシールランドを非接触にしたり、軽接触タイプのオイルシールを採用したりする傾向にある。そのため、構造上、図６に示すように軸受本体と前蓋１６ａ、後蓋１６ｂが軸受２から分離しやすい。このような分離が車軸への圧入組込み時に起きると、取扱いが煩雑になるため作業能率が悪く、場合によっては製品落下による品質不具合を発生させる可能性もあった。   Recently, as the speed of railway vehicles has increased, the seal lip and seal land have been made non-contact and light contact type oil seals have been adopted to reduce heat generation of the bearing while maintaining the sealing performance of the seal. is there. Therefore, structurally, the bearing main body, the front lid 16a, and the rear lid 16b are easily separated from the bearing 2 as shown in FIG. If such separation occurs during press fitting into the axle, the handling becomes complicated and the work efficiency is poor, and in some cases, there is a possibility of causing a quality defect due to a product drop.

この発明の目的は、前蓋や後蓋が軸受本体から容易に分離しないようにすることにある。   An object of the present invention is to prevent the front lid and the rear lid from being easily separated from the bearing body.

この発明の複列円すいころ軸受装置は、それぞれ外周に軌道をもった一対の内輪と、内周に２列の軌道をもった外輪と、内輪の軌道と外輪の軌道との間に介在させた２列の円すいころと、各列の円すいころを保持する保持器と、前記一対の内輪の軸方向両側に位置する環状部材と、前記外輪の両端部に配置した密封装置とを具備し、前記内輪と前記環状部材を、軸方向および半径方向のすきまをもって凹凸嵌合させたことを特徴とする。   The double-row tapered roller bearing device of the present invention is interposed between a pair of inner rings each having a track on the outer periphery, an outer ring having two rows of tracks on the inner periphery, and a track of the inner ring and a track of the outer ring. Two rows of tapered rollers, a cage for holding each row of tapered rollers, annular members positioned on both axial sides of the pair of inner rings, and sealing devices disposed at both ends of the outer ring, The inner ring and the annular member are ruggedly fitted with clearances in the axial direction and the radial direction.

請求項２の発明は、請求項１の複列円すいころ軸受において、前記すきまに軸受封入グリースを塗布したことを特徴とするものである。   According to a second aspect of the present invention, in the double row tapered roller bearing according to the first aspect, a bearing sealing grease is applied to the clearance.

請求項３の発明は、請求項１の複列円すいころ軸受において、前記内輪と前記環状部材との間に黄銅板を介在させ、前記半径方向すきまを前記黄銅板よりも外径側に配置したことを特徴とするものである。   According to a third aspect of the present invention, in the double row tapered roller bearing of the first aspect, a brass plate is interposed between the inner ring and the annular member, and the radial clearance is disposed on the outer diameter side of the brass plate. It is characterized by this.

請求項４の発明は、請求項１から３のいずれか１項の複列円すいころ軸受において、鉄道車両車軸用であって、前記環状部材が前蓋と後蓋であることを特徴とするものである。   The invention according to claim 4 is the double row tapered roller bearing according to any one of claims 1 to 3, wherein the annular member is a front lid and a rear lid. It is.

この発明によれば、前蓋と後蓋が内輪から分離しにくくなる。したがって、前蓋および後蓋を含めた軸受全体がユニットハンドリング可能な、取扱いが容易な複列円すいころ軸受装置を提供することができる。   According to this invention, it becomes difficult to separate the front lid and the rear lid from the inner ring. Therefore, it is possible to provide a double-row tapered roller bearing device that can be easily handled by the entire bearing including the front lid and the rear lid and can be handled as a unit.

以下、図面に従ってこの発明の実施の形態を説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１に複列円すいころ軸受を用いた鉄道車両車軸用軸受の縦断面を示す。複列円すいころ軸受２０は、一対の内輪２２と、外輪２４と、２列の転動体（円すいころ）２６と、保持器２８とで構成されている。内輪２２は車軸（図示せず）の軸端部に圧入するようになている。一対の内輪２２を挟んで軸方向両側に、環状部材すなわち前蓋４２と後蓋４４を配置して、ボルトやナットを用いて前蓋４２を車軸に締め付けることにより、一対の内輪２２の、ひいては軸受全体の位置決め、固定をする。外輪２４は軸箱（図示せず）に固定する。一対の内輪２２間に間座を介在させる場合もある。   FIG. 1 shows a longitudinal section of a railway vehicle axle bearing using a double-row tapered roller bearing. The double-row tapered roller bearing 20 includes a pair of inner rings 22, an outer ring 24, two rows of rolling elements (tapered rollers) 26, and a cage 28. The inner ring 22 is press-fitted into a shaft end portion of an axle (not shown). An annular member, that is, a front lid 42 and a rear lid 44 are arranged on both sides in the axial direction across the pair of inner rings 22, and the front lid 42 is fastened to the axle by using bolts and nuts. Position and fix the entire bearing. The outer ring 24 is fixed to a shaft box (not shown). In some cases, a spacer is interposed between the pair of inner rings 22.

図示した実施の形態の場合、前蓋４２と後蓋４４が環状部材に該当するが、内輪２２と前蓋４２との間に油切りを介在させることもある。また、後蓋４４に加えて、または後蓋４４に代えて、スリンガを設けることもある。   In the case of the illustrated embodiment, the front lid 42 and the rear lid 44 correspond to annular members, but oil draining may be interposed between the inner ring 22 and the front lid 42. Further, a slinger may be provided in addition to or instead of the rear lid 44.

外輪２４の両端部に密封装置３０が配置してあり、軸受内部に封入したグリースの洩れや、外部から異物が侵入するのを防止する役割を果たす。図１の右側の密封装置部分を拡大して示す図２を参照すると、密封装置３０は、シールケース３２と、シール本体３６と、シールスリーブ３８を主要な構成要素として含んでいる。   Sealing devices 30 are disposed at both ends of the outer ring 24 and serve to prevent leakage of grease sealed inside the bearing and intrusion of foreign matter from the outside. Referring to FIG. 2 showing an enlargement of the sealing device portion on the right side of FIG. 1, the sealing device 30 includes a seal case 32, a seal body 36, and a seal sleeve 38 as main components.

シールケース３２は外輪２４の端部開口内に圧入してある。シールケース３２の内面に芯金３４の円筒部が圧入してあり、この芯金３４を介してシール本体３６はシールケース３２に保持されている。シール本体３６はゴム製で、芯金３４の円板部に焼き付けてある。シール本体３６は３つのシールリップをもっている。すなわち、芯金３４から内径側に斜めに張り出した主リップ３６ａおよび副リップ３６ｂと、芯金３４からほぼ軸方向に張り出したダストリップ３６ｃとである。   The seal case 32 is press-fitted into the end opening of the outer ring 24. A cylindrical portion of the cored bar 34 is press-fitted into the inner surface of the seal case 32, and the seal main body 36 is held by the seal case 32 via the cored bar 34. The seal body 36 is made of rubber and is baked on the disk portion of the cored bar 34. The seal body 36 has three seal lips. In other words, the main lip 36a and the sub lip 36b projecting obliquely from the cored bar 34 toward the inner diameter side, and the dust lip 36c projecting substantially axially from the cored bar 34.

シールスリーブ３８の外周面は主リップ３６ａと副リップ３６ｂのためのシールランドを提供する。シールスリーブ３８は折り返し部３８ａを有し、その内周面がダストリップ３６ｃのためのシールランドを提供する。言い換えれば、主リップ３６ａと副リップ３６ｂはシールスリーブ３８の外周面に外径側から弾性的に、かつ軽く接触し、ガータースプリングは使用してない（軽接触タイプ）。ダストリップ３６ｃは折り返し部３８ａの内周面に内径側から弾性的に接触する。   The outer peripheral surface of the seal sleeve 38 provides a seal land for the main lip 36a and the sub lip 36b. The seal sleeve 38 has a folded portion 38a, and an inner peripheral surface thereof provides a seal land for the dust lip 36c. In other words, the main lip 36a and the sub lip 36b are in contact with the outer peripheral surface of the seal sleeve 38 elastically and lightly from the outer diameter side, and no garter spring is used (light contact type). The dust lip 36c elastically contacts the inner peripheral surface of the folded portion 38a from the inner diameter side.

シールケース３２の先端部とシールスリーブ３８の折り返し部３８ａとの間の環状のすきまがラビリンスシールを構成する。シールスリーブ３８のもう一方の端部は内径側に折り曲げて内向きフランジ３８ｂが形成してある。なお、符号４０で指してあるのは、軸受内部に充填したグリースが押し寄せるのを堰き止めるための堰板である。   An annular clearance between the tip of the seal case 32 and the folded portion 38a of the seal sleeve 38 forms a labyrinth seal. The other end of the seal sleeve 38 is bent to the inner diameter side to form an inward flange 38b. In addition, what is indicated by the reference numeral 40 is a dam plate for damming up the grease filled in the bearing.

以下の説明では、便宜上、一対の内輪２２のうち図１の左側すなわち車軸の軸端側の内輪２２をＡ列側内輪、図１の右側すなわち反軸端側の内輪２２をＢ列側内輪と呼ぶこととする。前蓋４２とＡ列側内輪２２、後蓋４４とＢ列側内輪２２を、それぞれ、半径方向および軸方向にすきまをもったルーズな凹凸嵌合とし、その嵌合部のすきまにグリースを塗布する。これにより、前蓋４２がＡ列側内輪２２から、後蓋４４がＢ列側内輪２２から分離して落下するという事態が起きにくくなる。したがって、図１に示す軸受装置全体がユニットハンドリング可能となり、とりわけエンドユーザでの取り扱いが容易になる。   In the following description, for convenience, among the pair of inner rings 22, the left side in FIG. 1, that is, the inner ring 22 on the axle end side of the axle is the A-row side inner ring, and the right side in FIG. I will call it. The front lid 42 and the A-row side inner ring 22 and the rear lid 44 and the B-row side inner ring 22 are loosely ruggedly fitted with clearances in the radial direction and the axial direction, respectively, and grease is applied to the gaps in the fitting portions. To do. This makes it difficult for the front lid 42 to fall from the A-row side inner ring 22 and the rear lid 44 to fall from the B-row side inner ring 22. Accordingly, the entire bearing device shown in FIG. 1 can be unit-handled, and in particular, it can be easily handled by the end user.

図１は、内輪２２の端面に凸部２２ａを形成し、前蓋４２および後蓋４４の端面に凹部４２ａ，４４ａを形成した例である。
具体的に述べると、前蓋４２の端面に凹部４２ａが形成してあり、Ａ列側内輪２２の端面に凸部２２ａが形状してある。そして、凹部４２ａと凸部２２ａを嵌合させた状態で、凹部４２ａの底面と凸部２２ａの端面との間に軸方向すきまδａが形成され、かつ、凹部４２ａの内周面と凸部２２ａの外周面との間に半径方向すきまδｂが形成されている。
また、後蓋４４の端面に凹部４４ａが形成してあり、Ｂ列側内輪２２の端面に凸部２２ａが形状してある。そして、凹部４４ａと凸部２２ａを嵌合させた状態で、凹部４４ａの底面と凸部２２ａの端面との間に軸方向すきまδａが形成され、かつ、凹部４４ａの内周面と凸部２２ａの外周面との間に半径方向すきまδｂが形成されている。
なお、凹凸嵌合の凹部と凸部の配置はここに例示したものとは逆、すなわち、内輪２２に凹部を形成し、前蓋４２、後蓋４４に凸部を形成することもできる。 FIG. 1 is an example in which a convex portion 22 a is formed on the end surface of the inner ring 22, and concave portions 42 a and 44 a are formed on the end surfaces of the front lid 42 and the rear lid 44.
More specifically, a concave portion 42 a is formed on the end surface of the front lid 42, and a convex portion 22 a is formed on the end surface of the A-row side inner ring 22. Then, in the state where the concave portion 42a and the convex portion 22a are fitted, an axial clearance δa is formed between the bottom surface of the concave portion 42a and the end surface of the convex portion 22a, and the inner peripheral surface of the concave portion 42a and the convex portion 22a. A radial clearance δb is formed between the outer circumferential surface and the outer circumferential surface.
Further, a concave portion 44 a is formed on the end surface of the rear lid 44, and a convex portion 22 a is formed on the end surface of the B row side inner ring 22. In the state where the concave portion 44a and the convex portion 22a are fitted, an axial clearance δa is formed between the bottom surface of the concave portion 44a and the end surface of the convex portion 22a, and the inner peripheral surface of the concave portion 44a and the convex portion 22a. A radial clearance δb is formed between the outer circumferential surface and the outer circumferential surface.
Note that the arrangement of the concave and convex portions of the concave and convex fitting is opposite to that illustrated here, that is, the concave portions can be formed in the inner ring 22 and the convex portions can be formed in the front lid 42 and the rear lid 44.

軸方向すきまδａおよび半径方向すきまδｂは共に０．１〜０．５ｍｍ程度とする。とくに半径方向すきまδｂに関しては、締め代を設けたタイトフィットとすると軸受の分解性が悪くなるため、専用の治具やプレス等が必要になり、点検時などに工数増加となる。したがって、ルーズフィット（すきまばめ）とするのが好ましい。   Both the axial clearance δa and the radial clearance δb are about 0.1 to 0.5 mm. In particular, with regard to the radial clearance δb, if a tight fit with a tightening margin is provided, the resolvability of the bearing is deteriorated, so that a dedicated jig, a press or the like is required, and the number of man-hours is increased during inspection. Therefore, it is preferable to have a loose fit.

嵌合部のすきまに塗布するグリースは軸受に封入する潤滑グリースと同じ種類であることが望ましい。軸受に封入する潤滑グリースの例としてはウレア系グリースが挙げられる。   It is desirable that the grease applied to the clearance of the fitting portion is the same type as the lubricating grease sealed in the bearing. An example of the lubricating grease to be sealed in the bearing is urea grease.

図２に示すように、内輪２２と後蓋４４との間に黄銅板４６を介在させてもよい。黄銅板４６はフレッティング対策用で、車軸のベンディングに伴う内輪２２と後蓋４４の接触面にフレッティング摩耗が発生するのを防止ないしは抑制する役割を果たす。黄銅板４６の外周に付加したゴムリップ４８を、内輪２２と後蓋４４との間に圧縮された状態で介在させることにより、万一摩耗粉が発生しても軸受内部に侵入するのを防止している。ここで図２に関連してＢ列側内輪２２と後蓋４４との嵌合部について言及したことは、Ａ列側内輪２２と前蓋４２との嵌合部についても同様にあてはまる。   As shown in FIG. 2, a brass plate 46 may be interposed between the inner ring 22 and the rear lid 44. The brass plate 46 serves as a countermeasure against fretting, and plays a role of preventing or suppressing the occurrence of fretting wear on the contact surface between the inner ring 22 and the rear lid 44 due to bending of the axle. A rubber lip 48 added to the outer periphery of the brass plate 46 is interposed between the inner ring 22 and the rear lid 44 in a compressed state, so that even if wear powder is generated, it can be prevented from entering the bearing. ing. The reference to the fitting portion between the B-row inner ring 22 and the rear lid 44 in relation to FIG. 2 applies similarly to the fitting portion between the A-row inner ring 22 and the front lid 42.

図２では凹凸嵌合部が黄銅板４６よりも内径側に配置してあるが、図３に示すように、凹凸嵌合部を黄銅板４６よりも外径側に配置することもできる。そうすることにより、Ｂ列側内輪２２と黄銅板４６との間および／または黄銅板４６と後蓋４４との間で摩耗が生じても、摩耗粉が軸受内部に侵入するのを防止する効果が一層高まる。ここで図３に関連してＢ列側内輪２２と後蓋４４との嵌合部について言及したことは、Ａ列側内輪２２と前蓋４２との嵌合部についても同様にあてはまる。   In FIG. 2, the concave / convex fitting portion is arranged on the inner diameter side of the brass plate 46, but the concave / convex fitting portion can also be arranged on the outer diameter side of the brass plate 46 as shown in FIG. 3. By doing so, even if wear occurs between the B-row side inner ring 22 and the brass plate 46 and / or between the brass plate 46 and the rear lid 44, the effect of preventing the wear powder from entering the inside of the bearing. Will further increase. The reference to the fitting portion between the B-row inner ring 22 and the rear lid 44 in relation to FIG. 3 also applies to the fitting portion between the A-row inner ring 22 and the front lid 42.

図４は、Ｂ列側内輪２２と後蓋４４とを機械的に分離可能に連結した例である。Ｂ列側内輪２２の大径側端面に凸部２２ａと環状溝２２ｂが形成してあり、凸部２２ａは円周方向の１箇所に切欠き２２ｃが設けてある。後蓋４４の端面にはＢ列側内輪２２の凸部２２ａとルーズに嵌合する凹部４４ａが形成してある。凹部５４ｂの円周方向の１箇所には、凹部４４ｂの外径から小径側に突出した突起４４ｂが形成してある。突起４４ｂの円周方方向の寸法は内輪２２の切欠き２２ｃを通過し得る程度で、突起４４ｂの軸方向寸法は内輪２２の環状溝２２ｂに沿って移動できる程度である。   FIG. 4 shows an example in which the B-row inner ring 22 and the rear lid 44 are mechanically separably connected. A convex portion 22a and an annular groove 22b are formed on the large-diameter side end face of the B-row inner ring 22, and the convex portion 22a is provided with a notch 22c at one place in the circumferential direction. On the end surface of the rear lid 44, a convex portion 22a of the B-row side inner ring 22 and a concave portion 44a that fits loosely are formed. A protrusion 44b protruding from the outer diameter of the recess 44b to the smaller diameter side is formed at one place in the circumferential direction of the recess 54b. The circumferential dimension of the protrusion 44 b is such that it can pass through the notch 22 c of the inner ring 22, and the axial dimension of the protrusion 44 b is such that it can move along the annular groove 22 b of the inner ring 22.

後蓋４４の突起４４ｂをＢ列側内輪２２の切欠き２２ｃに進入させて凹部４４ａと凸部２２ａを嵌合させた状態で、後蓋４４とＢ列側内輪２２を相対的に回転させると、突起４４ｂが凸部２２ａに係合して、両者は分離可能に連結されたことになる。つまり、軸方向に引いただけでは引き離せないが、切欠き２２ｃと突起４４ｂの位相が合うまで回して引き離せば分離することができる関係となる。したがって、この場合、グリースを塗布しなくても、後蓋４４の分離、落下が防止できる。   When the rear cover 44 and the B-row side inner ring 22 are relatively rotated while the protrusion 44b of the rear lid 44 is inserted into the notch 22c of the B-row side inner ring 22 and the concave portion 44a and the convex portion 22a are fitted to each other. Thus, the protrusion 44b is engaged with the convex portion 22a, and both are separably connected. That is, it cannot be separated only by pulling in the axial direction, but it can be separated by rotating until the notch 22c and the projection 44b are in phase with each other. Therefore, in this case, the rear cover 44 can be prevented from being separated and dropped without applying grease.

なお、切欠き２２ｃおよび突起４４ｂの配置は逆、すなわち、後蓋４４に切欠きを設け、Ｂ列側内輪２２に突起を設けてもよい。
ここで図４に関連してＢ列側内輪２２と後蓋４４との嵌合部について言及したことは、Ａ列側内輪２２と前蓋４２との嵌合部についても同様にあてはまる。 The arrangement of the notches 22c and the protrusions 44b may be reversed, that is, the rear lid 44 may be provided with a notch and the B row inner ring 22 may be provided with a protrusion.
Reference to the fitting portion between the B-row inner ring 22 and the rear lid 44 in relation to FIG. 4 also applies to the fitting portion between the A-row inner ring 22 and the front lid 42.

ここでは鉄道車両車軸用軸受として複列円すいころ軸受を例示したが、これに代えてその他の軸受たとえば複列円筒ころ軸受を使用したものにもこの発明を適用することができる。   Here, a double-row tapered roller bearing has been exemplified as a railway vehicle axle bearing, but the present invention can be applied to other bearings such as a double-row cylindrical roller bearing.

この発明の実施の形態を示す複列円すいころ軸受の縦断面図である。It is a longitudinal cross-sectional view of the double row tapered roller bearing which shows embodiment of this invention. 図１の要部拡大図である。It is a principal part enlarged view of FIG. 別の実施例を示す図２と類似の図である。It is a figure similar to FIG. 2 which shows another Example. （Ａ）は別の実施例を示す図２と類似の図、（Ｂ）は図４（Ａ）の内輪の端面図、（Ｃ）は図４（Ａ）の後蓋の端面図である。(A) is a view similar to FIG. 2 showing another embodiment, (B) is an end view of the inner ring of FIG. 4 (A), and (C) is an end view of the rear lid of FIG. 4 (A). 従来の技術を示す図１と類似の図である。It is a figure similar to FIG. 1 which shows a prior art. 従来の技術を示す鉄道車両車軸用軸受装置の縦断面図である。It is a longitudinal cross-sectional view of the bearing apparatus for railway vehicle axles which shows the prior art.

符号の説明Explanation of symbols

２２ 内輪
２２ａ 凸部
２２ｂ 環状溝
２２ｃ 切欠き
２４ 外輪
２６ 転動体（円すいころ）
２８ 保持器
３０ 密封装置
３２ シールケース
３４ 芯金
３６ シール本体
３６ａ 主リップ
３６ｂ 副リップ
３６ｃ ダストリップ
３８ シールスリーブ
３８ａ 折り返し部
３８ｂ 内向きフランジ
４０ 堰板
４２ 前蓋
４２ａ 凹部
４４ 後蓋
４４ａ 凹部
４４ｂ 突起
４６ 黄銅板
４８ ゴムリップ 22 Inner ring 22a Protruding part 22b Annular groove 22c Notch 24 Outer ring 26 Rolling element (tapered roller)
28 Cage 30 Sealing device 32 Seal case 34 Core metal 36 Seal body 36a Main lip 36b Sub lip 36c Dustrip 38 Seal sleeve 38a Folded part 38b Inward flange 40 Dam plate 42 Front lid 42a Concave 44 Rear lid 44a Concave 44b Protrusion 46 Brass plate 48 Rubber lip

Claims (4)

それぞれ外周に軌道をもった一対の内輪と、内周に２列の軌道をもった外輪と、内輪の軌道と外輪の軌道との間に介在させた２列の円すいころと、各列の円すいころを保持する保持器と、前記一対の内輪の軸方向両側に位置する環状部材と、前記外輪の両端部に配置した密封装置とを具備し、
前記内輪と前記環状部材を、軸方向および半径方向のすきまをもって凹凸嵌合させた複列円すいころ軸受装置。 A pair of inner rings each having a track on the outer periphery, an outer ring having two rows of tracks on the inner periphery, two rows of tapered rollers interposed between the track of the inner ring and the track of the outer ring, and a cone of each row A cage for holding rollers, annular members located on both axial sides of the pair of inner rings, and sealing devices disposed at both ends of the outer ring,
A double-row tapered roller bearing device in which the inner ring and the annular member are concavo-convexly fitted with clearances in an axial direction and a radial direction. 前記すきまに軸受封入グリースを塗布した請求項１の複列円すいころ軸受装置。   The double row tapered roller bearing device according to claim 1, wherein bearing clearance grease is applied to the gap. 前記内輪と前記環状部材との間に黄銅板を介在させ、前記半径方向すきまを前記黄銅板よりも外径側に配置した請求項１の複列円すいころ軸受装置。   The double-row tapered roller bearing device according to claim 1, wherein a brass plate is interposed between the inner ring and the annular member, and the radial clearance is disposed on the outer diameter side of the brass plate. 鉄道車両車軸用であって、前記環状部材が前蓋と後蓋である請求項１から３のいずれか１項の複列円すいころ軸受装置。   The double-row tapered roller bearing device according to any one of claims 1 to 3, wherein the annular member is a front lid and a rear lid.
JP2007108361A 2007-04-17 2007-04-17 Double row tapered roller bearing device Pending JP2008267431A (en)

Priority Applications (1)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011256965A (en) * 2010-06-10 2011-12-22 Ntn Corp Bearing device for axle of railway vehicle
JP2013019459A (en) * 2011-07-11 2013-01-31 Nsk Ltd Bearing device for railway vehicle axle
JP2018048658A (en) * 2016-09-20 2018-03-29 Ntn株式会社 Bearing device for axle
JP2019184064A (en) * 2018-04-06 2019-10-24 ナブテスコ株式会社 Seal mechanism and device including the same
CN114364894A (en) * 2019-08-16 2022-04-15 阿母斯替德铁路公司 Labyrinth seal with interlocking rotor and seal case insert

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60188060A (en) * 1984-03-08 1985-09-25 Meiji Milk Prod Co Ltd Live mold powder of bacterium belonging to genus bifidobacterium, having high resistance to acid in stomach, and its preparation
JPH08128452A (en) * 1994-10-31 1996-05-21 Ntn Corp Assembly of cylindrical roller bearing
JP2001254735A (en) * 2000-03-13 2001-09-21 Nachi Fujikoshi Corp Axle bearing
JP2005163815A (en) * 2003-11-28 2005-06-23 Ntn Corp Bearing with sealing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60188060A (en) * 1984-03-08 1985-09-25 Meiji Milk Prod Co Ltd Live mold powder of bacterium belonging to genus bifidobacterium, having high resistance to acid in stomach, and its preparation
JPH08128452A (en) * 1994-10-31 1996-05-21 Ntn Corp Assembly of cylindrical roller bearing
JP2001254735A (en) * 2000-03-13 2001-09-21 Nachi Fujikoshi Corp Axle bearing
JP2005163815A (en) * 2003-11-28 2005-06-23 Ntn Corp Bearing with sealing

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011256965A (en) * 2010-06-10 2011-12-22 Ntn Corp Bearing device for axle of railway vehicle
JP2013019459A (en) * 2011-07-11 2013-01-31 Nsk Ltd Bearing device for railway vehicle axle
JP2018048658A (en) * 2016-09-20 2018-03-29 Ntn株式会社 Bearing device for axle
WO2018056000A1 (en) * 2016-09-20 2018-03-29 Ntn株式会社 Bearing device for axle
GB2569494A (en) * 2016-09-20 2019-06-19 Ntn Toyo Bearing Co Ltd Bearing device for axle
GB2569494B (en) * 2016-09-20 2022-02-09 Ntn Toyo Bearing Co Ltd Bearing device for axle
JP2019184064A (en) * 2018-04-06 2019-10-24 ナブテスコ株式会社 Seal mechanism and device including the same
CN114364894A (en) * 2019-08-16 2022-04-15 阿母斯替德铁路公司 Labyrinth seal with interlocking rotor and seal case insert
CN114364894B (en) * 2019-08-16 2024-04-02 阿母斯替德铁路公司 Labyrinth seal with interlocking rotor and seal case insert

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