JP2016142364A - Bearing device for railway vehicle - Google Patents

Bearing device for railway vehicle Download PDF

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Publication number
JP2016142364A
JP2016142364A JP2015019419A JP2015019419A JP2016142364A JP 2016142364 A JP2016142364 A JP 2016142364A JP 2015019419 A JP2015019419 A JP 2015019419A JP 2015019419 A JP2015019419 A JP 2015019419A JP 2016142364 A JP2016142364 A JP 2016142364A
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Japan
Prior art keywords
inner ring
sleeve
spacer
peripheral surface
bearing device
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JP2015019419A
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Japanese (ja)
Inventor
鈴木　健吾
Kengo Suzuki
健吾 鈴木
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2015019419A priority Critical patent/JP2016142364A/en
Priority to PCT/JP2016/050185 priority patent/WO2016125516A1/en
Publication of JP2016142364A publication Critical patent/JP2016142364A/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
    • 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
    • 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
    • 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
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7826—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of the opposing surface cooperating with the seal, e.g. a shoulder surface of a bearing ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • 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

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device for a railway vehicle which inhibits wear caused by fretting and enables easy assembly work to an axle.SOLUTION: A bearing device 1 for a railway vehicle includes: a bearing 2 including an inner ring 7 having a raceway 6 on an outer peripheral surface, an outer ring 9 having a raceway 8 on an inner peripheral surface, and rolling elements 10 which are held between the raceway 6 of the inner ring 7 and the raceway 8 of the outer ring 9 so as to roll; a sealing device 12 configured to seal a space between the inner ring 7 and the outer ring 9; a front lid 3 and a rear lid 4 for fixing the bearing 2 to an axle S; and a spacer 5 disposed between the inner ring 7 of the bearing 2 and the rear lid 4. Part of the spacer 5 fits in an outer peripheral surface of the inner ring 7.SELECTED DRAWING: Figure 1

Description

本発明は、例えば鉄道車両の車軸に用いられる軸受装置に関する。   The present invention relates to a bearing device used for an axle of a railway vehicle, for example.

従来、鉄道車両の車軸に使用される軸受装置として、円すいころ軸受と、車軸に対して円すいころ軸受の位置決めを行う前蓋及び後蓋とを備えたものがある。この軸受装置における円すいころ軸受は、外周面に軌道を有する一対の内輪と、内周面に複列の軌道を有する外輪と、内輪の軌道と外輪の軌道との間で転動可能に保持される円すいころと、軸受内部に充填されるグリースの漏れを防止するとともに、異物が軸受内部に侵入することを防止する密封装置（オイルシール）とを備える。この軸受装置では、前蓋が一対の内輪のうちの一方に当接し、後ろ蓋が他方の内輪に当接することにより、円すいころ軸受を車軸の所定位置に固定している（例えば特許文献１参照）。   2. Description of the Related Art Conventionally, a bearing device used for an axle of a railway vehicle includes a tapered roller bearing and a front lid and a rear lid that position the tapered roller bearing with respect to the axle. The tapered roller bearing in this bearing device is held so as to be able to roll between a pair of inner rings having raceways on the outer peripheral surface, an outer ring having double-row raceways on the inner peripheral surface, and a raceway of the inner ring and outer raceway. And a sealing device (oil seal) for preventing leakage of grease filled in the bearing and preventing foreign matter from entering the bearing. In this bearing device, the front lid is in contact with one of the pair of inner rings and the rear cover is in contact with the other inner ring, so that the tapered roller bearing is fixed at a predetermined position of the axle (see, for example, Patent Document 1). ).

上記のような鉄道車両用軸受装置では、車軸に鉄道車両特有の過大なラジアル荷重が負荷されると、この車軸に過大な曲げモーメントが作用し、車軸の撓み（ベンディング）が生じる。このように車軸が撓んだ状態で回転する結果、内輪と後蓋の接触部分に繰り返し応力が発生し、接触部分が摩耗する（フレッティング）ことになる。   In the railway vehicle bearing device as described above, when an excessive radial load peculiar to the railway vehicle is applied to the axle, an excessive bending moment acts on the axle, causing bending (bending) of the axle. As a result of rotating the axle in a bent state, stress is repeatedly generated at the contact portion between the inner ring and the rear cover, and the contact portion is worn (fretting).

フレッティングによる摩耗は、車軸に過大なラジアル荷重が負荷される鉄道車両にとって不可避なものであり、この摩耗が進行すると、軸受装置の軸方向精度が低下し、発生した摩耗粉が車軸軸受の内部に侵入して軸受内の潤滑剤を劣化させ、軸受装置の寿命を短くする原因となる。このようなフレッティングによる摩耗を抑制するため、同文献の軸受装置では、内輪と後蓋との間に環状スペーサを介在させている。   Wear caused by fretting is unavoidable for railway vehicles in which an excessive radial load is applied to the axle, and as this wear progresses, the axial accuracy of the bearing device decreases, and the generated wear powder is generated inside the axle bearing. This will cause the lubricant in the bearing to deteriorate and deteriorate the life of the bearing device. In order to suppress such wear due to fretting, in the bearing device of this document, an annular spacer is interposed between the inner ring and the rear lid.

特開２００４−３３２９０５号公報JP 2004-332905 A

上記のような従来の軸受装置では、車軸に組み付ける際に、内輪と車軸との間にスティックスリップが生じる場合がある。スティックスリップとは、摩擦面間に生ずる微視的な摩擦面の付着、滑りの繰り返しによって引き起こされる自励振動をいい、内輪を車軸に圧入する際に生じ得る。スティックスリップが生じると、その振動により、車軸に挿通した環状スペーサが斜めに倒れ込んでしまい、その位置決めをすることができずに組み付け作業が困難になる場合があった。   In the conventional bearing device as described above, stick slip may occur between the inner ring and the axle when assembled to the axle. Stick-slip refers to self-excited vibration caused by microscopic adhesion between the friction surfaces and repeated sliding, and can occur when the inner ring is pressed into the axle. When stick-slip occurs, the vibration causes the annular spacer inserted through the axle to tilt down, making it difficult to position the assembly and making the assembly work difficult.

本発明は、上記の事情に鑑みてなされたものであり、フレッティングによる摩耗を抑制するとともに、車軸への組み付け作業を容易に行うことが可能な鉄道車両用軸受装置を提供することを目的とする。   The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a railway vehicle bearing device that can suppress wear due to fretting and can be easily assembled to an axle. To do.

本発明に係る鉄道車両用軸受装置は、上記の課題を解決するためのものであって、外周面に軌道を有する内輪と、内周面に軌道を有する外輪と、前記内輪の前記軌道と前記外輪の前記軌道との間で転動可能に保持される転動体とを有する軸受と、前記軸受を車軸に固定するための前蓋及び後蓋と、前記内輪と前記後蓋との間に介在するスペーサと、を備え、前記スペーサの一部が前記内輪の外周面に嵌合するように構成されるものである。   A railcar bearing device according to the present invention is for solving the above-described problem, and includes an inner ring having a track on an outer peripheral surface, an outer ring having a track on an inner peripheral surface, the track of the inner ring, and the A bearing having a rolling element that is rotatably held between the outer ring and the raceway, a front lid and a rear lid for fixing the bearing to an axle, and an intermediate between the inner ring and the rear lid. And a part of the spacer is configured to be fitted to the outer peripheral surface of the inner ring.

このように、スペーサを内輪と後蓋との間に介在させることにより、内輪と後蓋の間のフレッティングによる摩耗を抑制できる。この場合、スペーサの一部を内輪の外周面に嵌合させることで、このスペーサの位置決め及び固定を確実に行うことができる。このようにスペーサを内輪に固定することにより、軸受装置の車軸への組み付けの際に、スティックスリップが生じたとしても、スペーサが倒れ込むということが確実に防止され、この組み付け作業を容易に効率良く行うことが可能になる。   Thus, by interposing the spacer between the inner ring and the rear lid, it is possible to suppress wear due to fretting between the inner ring and the rear lid. In this case, the spacer can be reliably positioned and fixed by fitting a part of the spacer to the outer peripheral surface of the inner ring. By fixing the spacer to the inner ring in this way, even if stick slip occurs when the bearing device is assembled to the axle, the spacer is reliably prevented from falling down, and this assembling work can be performed easily and efficiently. It becomes possible to do.

また、上記構成において、前記スペーサの一部は、前記内輪の外周面に嵌合するスリーブとして構成され、前記軸受は、前記外輪の前記内周面に取り付けられるとともに、前記スリーブに摺接するシール本体を備えることが好ましい。   In the above configuration, a part of the spacer is configured as a sleeve that fits to the outer peripheral surface of the inner ring, and the bearing is attached to the inner peripheral surface of the outer ring, and the seal body that is in sliding contact with the sleeve It is preferable to provide.

このように、スペーサの一部をスリーブとして内輪の外周面に嵌合させるとともに、このスリーブにシール本体を摺接させることにより、内輪と外輪の間を密封（シール）することが可能になる。さらに、シール本体は、内輪の外周面に摺接することがないため、内輪が摩耗することも防止できる。   As described above, a part of the spacer is fitted as a sleeve to the outer peripheral surface of the inner ring, and the seal main body is slidably contacted with the sleeve, thereby sealing (sealing) the inner ring and the outer ring. Furthermore, since the seal body does not slidably contact the outer peripheral surface of the inner ring, the inner ring can be prevented from being worn.

また、上記構成において、前記スペーサは、前記スリーブから半径方向内方に突出するとともに前記内輪の端面と前記後蓋の端面の双方に接触する内側突出部を備えることが好ましい。この内側突出部が内輪の端面と後蓋の端面に当接することによって、内輪と後蓋とのフレッティングによる摩耗を抑制することが可能になる。   In the above configuration, it is preferable that the spacer includes an inner protrusion that protrudes radially inward from the sleeve and contacts both the end surface of the inner ring and the end surface of the rear lid. When the inner protrusion comes into contact with the end surface of the inner ring and the end surface of the rear lid, it is possible to suppress wear due to fretting between the inner ring and the rear lid.

また、軸受装置は、前記スリーブから半径方向外方に突出するとともに、軸受内部側で前記シール本体を覆う外側突出部を備えることが好ましい。これによって、車軸の回転中に軸受内部に封入されているグリース等の潤滑剤が飛散した場合に、この潤滑剤はこの外側突出部に接触することになり、外側突出部は飛散した潤滑剤がシール本体に付着することを防止する。これによって、シール本体のシール機能を長期にわたって維持することが可能になる。   In addition, the bearing device preferably includes an outer protrusion that protrudes radially outward from the sleeve and covers the seal body on the inner side of the bearing. As a result, when a lubricant such as grease encapsulated inside the bearing is scattered during the rotation of the axle, the lubricant comes into contact with the outer protruding portion, and the outer protruding portion has the scattered lubricant. Prevents sticking to the seal body. This makes it possible to maintain the sealing function of the seal body over a long period of time.

また、フレッティングによる摩耗に対する耐摩耗性を十分に確保するために、前記スペーサは、鋼材又は黄銅により構成されることが望ましい。この場合、スペーサの一部であるスリーブも同じ材料で構成することにより、シール本体の摺接に対するスリーブの耐摩耗性も十分に確保され得る。   In addition, in order to sufficiently ensure wear resistance against wear due to fretting, the spacer is preferably made of steel or brass. In this case, the sleeve, which is a part of the spacer, is also made of the same material, so that the wear resistance of the sleeve against the sliding contact of the seal body can be sufficiently secured.

また、本発明に係る軸受装置によれば、前記スリーブの内周面と前記内輪の前記外周面との間に弾性体による環状部材を介在させることが望ましい。   Further, according to the bearing device of the present invention, it is desirable that an annular member made of an elastic body be interposed between the inner peripheral surface of the sleeve and the outer peripheral surface of the inner ring.

通常、内輪と車軸の寸法関係はしまりばめとなるように設計されており、スリーブを内輪の外周面に嵌合することによって、この部分において局部的に面圧が高くなって、車軸の局部的な摩耗の原因となるおそれがある。上記のように弾性変形可能な環状部材をスリーブと内輪との間に介在させることで、スリーブに内輪が圧入されたときに、この環状部材の弾性変形によってこの内輪の変形による車軸への影響を可及的に小さくすることが可能になる。   Usually, the dimensional relationship between the inner ring and the axle is designed to be an interference fit, and by fitting the sleeve to the outer peripheral surface of the inner ring, the surface pressure increases locally in this part, and the local part of the axle May cause general wear. By interposing an elastically deformable annular member between the sleeve and the inner ring as described above, when the inner ring is press-fitted into the sleeve, the elastic deformation of the annular member prevents the influence of the deformation of the inner ring on the axle. It becomes possible to make it as small as possible.

また、本発明に係る軸受装置によれば、フレッティングによる摩耗に対する耐摩耗性を向上させるために、前記スペーサにダイヤモンドライクカーボンによる被膜を形成してもよい。この場合、スペーサの一部であるスリーブにも被膜を形成することにより、シール本体の摺接に対するスリーブの耐摩耗性も向上することになる。   According to the bearing device of the present invention, a diamond-like carbon film may be formed on the spacer in order to improve wear resistance against wear due to fretting. In this case, the abrasion resistance of the sleeve against the sliding contact of the seal body is also improved by forming a coating on the sleeve which is a part of the spacer.

以上のように、本発明によれば、フレッティングによる摩耗を抑制するとともに、軸受装置の車軸への組み付け作業を容易に行うことが可能になる。   As described above, according to the present invention, it is possible to suppress wear due to fretting and to easily perform the work of assembling the bearing device to the axle.

図１は、本発明に係る軸受装置の一実施形態を示す断面図である。FIG. 1 is a cross-sectional view showing an embodiment of a bearing device according to the present invention. 図２は、軸受装置の要部拡大断面図である。FIG. 2 is an enlarged cross-sectional view of a main part of the bearing device. 図３は、本発明に係る軸受装置の他の例を示す要部拡大断面図である。FIG. 3 is an enlarged sectional view of a main part showing another example of the bearing device according to the present invention. 図４は、本発明に係る軸受装置の他の例を示す要部拡大断面図である。FIG. 4 is an enlarged cross-sectional view showing a main part of another example of the bearing device according to the present invention. 図５は、本発明に係る軸受装置の他の例を示す要部拡大断面図である。FIG. 5 is an enlarged sectional view of a main part showing another example of the bearing device according to the present invention. 図６は、本発明に係る軸受装置の他の例を示す要部拡大断面図である。FIG. 6 is an enlarged cross-sectional view showing a main part of another example of the bearing device according to the present invention.

以下、本発明に係る鉄道車両用軸受装置（以下、単に「軸受装置」という）を実施するための形態について、図面を参照しながら説明する。図１及び図２は、本発明に係る軸受装置の一実施形態を示す。   DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out a railway vehicle bearing device (hereinafter simply referred to as “bearing device”) according to the present invention will be described with reference to the drawings. 1 and 2 show an embodiment of a bearing device according to the present invention.

図１は、軸受装置１を鉄道車両の車軸Ｓに組み付けた例を示す。軸受装置１は、円すいころ軸受２と、円すいころ軸受２を固定するための前蓋３および後蓋４と、円すいころ軸受２と後蓋４との間に介在する環状のスペーサ５とを備える。   FIG. 1 shows an example in which the bearing device 1 is assembled to an axle S of a railway vehicle. The bearing device 1 includes a tapered roller bearing 2, a front lid 3 and a rear lid 4 for fixing the tapered roller bearing 2, and an annular spacer 5 interposed between the tapered roller bearing 2 and the rear lid 4. .

なお、本明細書では、車軸Ｓの軸方向端部寄りの位置を「前」又は「前側」といい、この前（側）よりも車軸Ｓの軸方向中央寄りの位置を「後」又は「後側」という。また、本明細書において、「半径方向」とは、基本的には車軸Ｓの半径方向をいうが、この車軸Ｓに同心状に配置される前蓋３、後蓋４、後述する円すいころ軸受２における内輪７、外輪９、スリーブ２１，３１およびシールケース３３等の半径方向をいう場合もある。また、この半径方向において、その中心（車軸Ｓの軸心）から離れる方向を「半径方向外方」といい、その中心に向かう方向を「半径方向内方」という。また、相対的な位置関係を述べる場合において、半径方向内方側の位置を「内」又は「内側」といい、この内（側）よりも半径方向外方側の位置を「外」又は「外側」という。   In the present specification, a position near the axial end of the axle S is referred to as “front” or “front side”, and a position closer to the center in the axial direction of the axle S than the front (side) is referred to as “rear” or “ It is called "the rear side". In the present specification, the “radial direction” basically refers to the radial direction of the axle S, but the front lid 3 and the rear lid 4 that are concentrically arranged on the axle S, and a tapered roller bearing described later. 2 may also refer to the radial direction of the inner ring 7, the outer ring 9, the sleeves 21 and 31, the seal case 33 and the like. Further, in this radial direction, a direction away from the center (axial center of the axle S) is referred to as “radially outward”, and a direction toward the center is referred to as “radially inward”. In the case of describing the relative positional relationship, the position on the radially inner side is referred to as “inside” or “inside”, and the position on the radially outer side from this inside (side) is referred to as “outside” or “ It is called “outside”.

円すいころ軸受２は、外周面に円すい状の軌道６を有する一対の内輪７ｆ，７ｒと、内周面に円すい状の軌道８を有する外輪９と、内輪７の軌道６と外輪９の軌道８との間に転動自在に設けられる複数の円すいころ（転動体）１０と、各円すいころ１０を所定の間隔をおいて転動可能に保持する保持器１１ｆ，１１ｒと、内輪７ｆ，７ｒと外輪９との間を密封する密封装置（オイルシール）１２ｆ，１２ｒとを備える。   The tapered roller bearing 2 includes a pair of inner rings 7f and 7r having a tapered raceway 6 on the outer peripheral surface, an outer ring 9 having a tapered raceway 8 on the inner peripheral surface, a raceway 6 of the inner ring 7 and a raceway 8 of the outer ring 9. A plurality of tapered rollers (rolling elements) 10 that are provided so as to roll freely, retainers 11f and 11r that hold the tapered rollers 10 at predetermined intervals so that they can roll, and inner rings 7f and 7r, Sealing devices (oil seals) 12f and 12r for sealing between the outer ring 9 are provided.

各内輪７ｆ，７ｒは、その軌道６を挟むように、一端部に小つば１４を有し、他端部に大つば１５を有する。各内輪７ｆ，７ｒは、軌道６に円すいころ１０の側面（転動面）を接触させるとともに、小つば１４と大つば１５との間で円すいころ１０が転動するようにこの円すいころ１０を保持している。なお、一対の内輪７ｆ，７ｒの間には、間座１３が設けられている。   Each inner ring 7f, 7r has a small brim 14 at one end and a large brim 15 at the other end so as to sandwich the track 6. Each of the inner rings 7f and 7r brings the tapered roller 10 into contact with the raceway 6 so that the side surface (rolling surface) of the tapered roller 10 is brought into contact, and the tapered roller 10 rolls between the small collar 14 and the large collar 15. keeping. A spacer 13 is provided between the pair of inner rings 7f and 7r.

外輪９は、その内周面に、円すい状に構成される複列の軌道８と、環状凹部１６ｆ，１６ｒとを有する。環状凹部１６ｆ，１６ｒは、外輪９の軸心方向における両端部（前端部及び後端部）に形成されている。また、外輪９の軸心方向中央部には、軸受内圧を解放するための空気抜栓１７が設けられている。   The outer ring 9 has a double-row track 8 configured in a conical shape and annular recesses 16f and 16r on its inner peripheral surface. The annular recesses 16 f and 16 r are formed at both end portions (front end portion and rear end portion) in the axial direction of the outer ring 9. In addition, an air vent 17 for releasing the bearing internal pressure is provided at the axial center of the outer ring 9.

複数の円すいころ１０は、一対の内輪７ｆ，７ｒの軌道６及び外輪９の複列の軌道８に対応して、複列に配列されている。各円すいころ１０は、大径端部１８と小径端部１９とを有する。複列に配列される円すいころ１０において、一方の列における円すいころ１０の小径端部１９と他方の列における円すいころ１０の小径端部１９とが対向するように配置される。   The plurality of tapered rollers 10 are arranged in a double row corresponding to the raceway 6 of the pair of inner rings 7 f and 7 r and the double row raceway 8 of the outer ring 9. Each tapered roller 10 has a large-diameter end 18 and a small-diameter end 19. In the tapered rollers 10 arranged in a double row, the small diameter ends 19 of the tapered rollers 10 in one row and the small diameter ends 19 of the tapered rollers 10 in the other row are arranged to face each other.

保持器１１ｆ，１１ｒは、一対の内輪７ｆ，７ｒの軌道６及び外輪９の複列の軌道８に対応するように、前側の保持器１１ｆと後側の保持器１１ｒとを含む。各保持器１１ｆ，１１ｒは、環状（筒状）に構成されるとともに、複数の円すいころ１０を円周方向において等間隔で保持する。各保持器１１ｆ，１１ｒは、各円すいころ１０の間隔を維持しつつ、各円すいころ１０の転動可能に保持するポケット２０を有する。   The retainers 11f and 11r include a front retainer 11f and a rear retainer 11r so as to correspond to the track 6 of the pair of inner rings 7f and 7r and the double-row track 8 of the outer ring 9. Each retainer 11f, 11r is configured in an annular shape (cylindrical shape) and holds a plurality of tapered rollers 10 at equal intervals in the circumferential direction. Each retainer 11f, 11r has a pocket 20 that holds each tapered roller 10 in a rollable manner while maintaining the interval between the tapered rollers 10.

図１に示すように、密封装置１２ｆ，１２ｒは、円すいころ軸受２の前側で内輪７ｆと外輪９との間を密封する第１密封装置１２ｆと、円すいころ軸受２の後側で内輪７ｒと外輪９との間を密封する第２密封装置１２ｒとを含む。   As shown in FIG. 1, the sealing devices 12f and 12r include a first sealing device 12f that seals between the inner ring 7f and the outer ring 9 on the front side of the tapered roller bearing 2, and an inner ring 7r on the rear side of the tapered roller bearing 2. And a second sealing device 12r for sealing between the outer ring 9.

第１密封装置１２ｆは、前側の内輪７ｆの外周面に嵌め込まれるスリーブ（以下「第１スリーブ」という）２１と、この第１スリーブ２１に摺接するシール本体（以下「第１シール本体」という）２２とを備える。   The first sealing device 12f includes a sleeve (hereinafter referred to as “first sleeve”) 21 fitted to the outer peripheral surface of the front inner ring 7f, and a seal body (hereinafter referred to as “first seal body”) slidably in contact with the first sleeve 21. 22.

第１スリーブ２１は、例えば、黄銅板、高力黄銅鋳物、冷間圧延鋼板、熱間圧延軟鋼板、高張力鋼板、ステンレス鋼板、高溶融めっき鋼板等によって製造され得る。第１スリーブ２１の板厚は０．８ｍｍ〜２．０ｍｍとされることが望ましいが、この板厚に限定されるものではない。   The first sleeve 21 can be made of, for example, a brass plate, a high-strength brass casting, a cold-rolled steel plate, a hot-rolled mild steel plate, a high-tensile steel plate, a stainless steel plate, a high hot-dip plated steel plate, or the like. The plate thickness of the first sleeve 21 is desirably 0.8 mm to 2.0 mm, but is not limited to this plate thickness.

第１スリーブ２１は、前側の内輪７ｆにおける大つば１５の外周面に嵌合されている。この第１スリーブ２１は直線状の内側円筒部２３と、この内側円筒部２３から半径方向外方に突出する環状の外側突出部２４と、この外側突出部２４の半径方向外端部から後方に突出する外側円筒部２５とを備える。   The first sleeve 21 is fitted to the outer peripheral surface of the large brim 15 in the front inner ring 7f. The first sleeve 21 includes a linear inner cylindrical portion 23, an annular outer protruding portion 24 that protrudes radially outward from the inner cylindrical portion 23, and a rearward direction from the radially outer end of the outer protruding portion 24. And a projecting outer cylindrical portion 25.

第１シール本体２２は、芯金２６と、この芯金２６に一体に形成される弾性シール２７とを備える。芯金２６は、外輪９に取り付けられる円筒状の取付部２８と、弾性シール２７を支持する支持部２９とを備える。取付部２８は、外輪９における前側の環状凹部１６ｆに嵌め込まれている。支持部２９は、取付部２８の一端部（前端部）から半径方向内方に突出する円環状に構成される。   The first seal body 22 includes a metal core 26 and an elastic seal 27 formed integrally with the metal core 26. The core metal 26 includes a cylindrical attachment portion 28 attached to the outer ring 9 and a support portion 29 that supports the elastic seal 27. The attachment portion 28 is fitted into the front annular recess 16 f of the outer ring 9. The support portion 29 is formed in an annular shape that protrudes inward in the radial direction from one end portion (front end portion) of the attachment portion 28.

弾性シール２７は、ゴム製であり、焼き付けによって支持部２９と一体に構成される。弾性シール２７は、３つのシールリップ３０を備える。３つのシールリップ３０のうち、１つのシールリップ３０は、第１スリーブ２１における外側円筒部２５の内周面に近接している。   The elastic seal 27 is made of rubber and is configured integrally with the support portion 29 by baking. The elastic seal 27 includes three seal lips 30. Of the three seal lips 30, one seal lip 30 is close to the inner peripheral surface of the outer cylindrical portion 25 of the first sleeve 21.

残りの２つのシールリップ３０のうち、１つのシールリップ３０は、第１スリーブ２１の内側円筒部２３の外周面に近接しており、もう１つのシールリップ３０は、内側円筒部２３の外周面に接触している。なお、第１スリーブ２１の外側突出部２４及び外側円筒部２５は第１シール本体２２の弾性シール２７を覆うカバー部としても機能する。   Of the remaining two seal lips 30, one seal lip 30 is close to the outer peripheral surface of the inner cylindrical portion 23 of the first sleeve 21, and the other seal lip 30 is the outer peripheral surface of the inner cylindrical portion 23. Touching. The outer projecting portion 24 and the outer cylindrical portion 25 of the first sleeve 21 also function as a cover portion that covers the elastic seal 27 of the first seal body 22.

図２は、第２密封装置１２ｒの拡大断面図を示す。図１、図２に示すように、第２密封装置１２ｒは、後側の内輪７ｒの外周面に嵌合されるスリーブ（以下「第２スリーブ」という）３１と、この第２スリーブ３１に摺接するシール本体（以下「第２シール本体」という）３２と、第２シール本体３２を収納するシールケース３３とを備える。   FIG. 2 shows an enlarged cross-sectional view of the second sealing device 12r. As shown in FIGS. 1 and 2, the second sealing device 12r includes a sleeve (hereinafter referred to as “second sleeve”) 31 fitted to the outer peripheral surface of the rear inner ring 7r, and the second sleeve 31. A seal main body (hereinafter referred to as “second seal main body”) 32 and a seal case 33 for accommodating the second seal main body 32 are provided.

第２スリーブ３１は、直線状の円筒形状に構成されており、後側の内輪７ｒにおける大つば１５の外周面に嵌め込まれている。この第２スリーブ３１の後端部には、スペーサ５が一体に設けられている。スペーサ５は、第２スリーブ３１の後端部から半径方向内方に突出する内側突出部として構成される。   The second sleeve 31 has a linear cylindrical shape and is fitted on the outer peripheral surface of the large collar 15 in the rear inner ring 7r. The spacer 5 is integrally provided at the rear end portion of the second sleeve 31. The spacer 5 is configured as an inner protrusion that protrudes radially inward from the rear end of the second sleeve 31.

一体に構成されるスペーサ５と第２スリーブ３１は、例えば、黄銅板、高力黄銅鋳物、冷間圧延鋼板、熱間圧延軟鋼板、高張力鋼板、ステンレス鋼板、高溶融めっき鋼板等によって製造され得る。スペーサ５及び第２スリーブ３１の板厚は、第１スリーブ２１と同様に、０．８ｍｍ〜２．０ｍｍとされることが望ましいが、この板厚に限定されるものではない。   The integrally configured spacer 5 and the second sleeve 31 are made of, for example, a brass plate, a high-strength brass casting, a cold-rolled steel plate, a hot-rolled mild steel plate, a high-tensile steel plate, a stainless steel plate, a high-melt-plated steel plate, or the like. obtain. The plate thickness of the spacer 5 and the second sleeve 31 is desirably 0.8 mm to 2.0 mm, as with the first sleeve 21, but is not limited to this plate thickness.

スペーサ５は、第２スリーブ３１が後側の内輪７ｒにおける大つば１５に取り付けられたときに、その一方の面、すなわち前側の面がこの内輪７ｒの後端部（後端面）に接触する。また、スペーサ５の他方の面、すなわち後側の面は、後蓋４の前端部（前端面）に接触している。したがって、このスペーサ５は、後側の内輪７ｒの後端部と後蓋４の前端部とによって挟まれた状態となっている。   When the second sleeve 31 is attached to the large collar 15 of the rear inner ring 7r, one surface, that is, the front surface of the spacer 5 comes into contact with the rear end portion (rear end surface) of the inner ring 7r. The other surface of the spacer 5, that is, the rear surface, is in contact with the front end portion (front end surface) of the rear lid 4. Therefore, the spacer 5 is sandwiched between the rear end portion of the rear inner ring 7 r and the front end portion of the rear lid 4.

第２スリーブ３１の表面には、シール本体３２の摺動に対する第２スリーブ３１の耐摩耗性を向上させるために、ダイヤモンドライクカーボン（ＤＬＣ）による被膜を形成してもよい。同様に、この被膜は、スペーサ５の両面に形成してもよい。これにより、後側の内輪７ｒと後蓋４とのフレッティングによる摩耗に対するスペーサ５の耐摩耗性が向上する。   A film made of diamond-like carbon (DLC) may be formed on the surface of the second sleeve 31 in order to improve the wear resistance of the second sleeve 31 against sliding of the seal body 32. Similarly, this coating may be formed on both sides of the spacer 5. Thereby, the wear resistance of the spacer 5 against wear due to fretting between the rear inner ring 7r and the rear lid 4 is improved.

第２シール本体３２は、第１シール本体２２と同様に、芯金３４と、弾性シール３５とを備える。芯金３４は、外輪９の後端部における環状凹部１６ｒに取り付けられる取付部３６と、弾性シール３５を支持する支持部３７とを備える。第２シール本体３２の取付部３６は、シールケース３３に嵌め込まれるとともに、このシールケース３３を介して外輪９の環状凹部１６ｒに取り付けられる。支持部３７は、取付部３６の一端部から半径方向内方に突出する円環状に構成される。   Similar to the first seal body 22, the second seal body 32 includes a cored bar 34 and an elastic seal 35. The core metal 34 includes an attachment portion 36 attached to the annular recess 16 r at the rear end portion of the outer ring 9 and a support portion 37 that supports the elastic seal 35. The attachment portion 36 of the second seal body 32 is fitted into the seal case 33 and attached to the annular recess 16r of the outer ring 9 via the seal case 33. The support portion 37 is configured in an annular shape that protrudes radially inward from one end portion of the attachment portion 36.

弾性シール３５は、ゴム製であり、焼き付けにより支持部３７と一体に構成される。また、弾性シール３５は、２つのシールリップ３８を備える。この２つのシールリップ３８のうち、一方のシールリップ３８は、第２スリーブ３１における第２スリーブ３１の外周面に近接しており、他方のシールリップ３８は、第２スリーブ３１の外周面に接触している。   The elastic seal 35 is made of rubber and is configured integrally with the support portion 37 by baking. The elastic seal 35 includes two seal lips 38. Of the two seal lips 38, one seal lip 38 is close to the outer peripheral surface of the second sleeve 31 in the second sleeve 31, and the other seal lip 38 is in contact with the outer peripheral surface of the second sleeve 31. doing.

シールケース３３は、外輪９の後端部における環状凹部１６ｒに嵌め込まれる円筒状の取付部３９と、この取付部３９の一端部から半径方向内方に突出する環状の内側突出部４０とを備える。取付部３９は、その内周面に第２シール本体３２の取付部３６が嵌合した状態で、外輪９の環状凹部１６ｒに嵌合している。このように、円すいころ軸受２は、第２シール本体３２の取付部３２とシールケース３３の取付部３９との二重の嵌合構造により、高い密封性を確保している。   The seal case 33 includes a cylindrical attachment portion 39 that is fitted into the annular recess 16r at the rear end portion of the outer ring 9, and an annular inner protrusion portion 40 that protrudes radially inward from one end portion of the attachment portion 39. . The attachment portion 39 is fitted in the annular recess 16r of the outer ring 9 in a state where the attachment portion 36 of the second seal main body 32 is fitted to the inner peripheral surface thereof. Thus, the tapered roller bearing 2 ensures high sealing performance by the double fitting structure of the mounting portion 32 of the second seal body 32 and the mounting portion 39 of the seal case 33.

シールケース３３の内側突出部４０は、第２シール本体３２を後側から覆うカバー部として機能する。この内側突出部４０は、その突出端部が第２スリーブ３１における外周面に近接するように構成される。これにより、内側突出部４０と第２スリーブ３１との間にラビリンスシールが形成されている。   The inner protruding portion 40 of the seal case 33 functions as a cover portion that covers the second seal body 32 from the rear side. The inner protruding portion 40 is configured such that the protruding end portion is close to the outer peripheral surface of the second sleeve 31. Thereby, a labyrinth seal is formed between the inner protrusion 40 and the second sleeve 31.

前蓋３は、車軸Ｓの端部を覆うためのものであり、車軸Ｓの端部の径よりも大径な円板状に構成される。前蓋３は、ボルト４１を挿通可能な挿通孔４２と、前側の内輪７ｆに当接する当接部４３とを備える。前蓋３は、車軸Ｓの端部に形成されたねじ穴４４にこの挿通孔４２を一致させ、この挿通孔４２を通じてボルト４１をねじ穴４４に螺合させることにより、車軸Ｓに固定される。このとき、前蓋３の当接部４３は、前側の内輪７ｆにおける前端部に当接する。   The front lid 3 is for covering the end of the axle S, and is configured in a disk shape having a diameter larger than the diameter of the end of the axle S. The front lid 3 includes an insertion hole 42 through which the bolt 41 can be inserted, and a contact portion 43 that contacts the front inner ring 7f. The front lid 3 is fixed to the axle S by aligning the insertion hole 42 with the screw hole 44 formed at the end of the axle S and screwing the bolt 41 into the screw hole 44 through the insertion hole 42. . At this time, the contact portion 43 of the front lid 3 contacts the front end portion of the inner ring 7f on the front side.

後蓋４は、円環状に構成されており、その内側に車軸Ｓが挿通されている。この後蓋４は、小径円筒部４５と、後方に向かうにつれて拡径するテーパ部４６と、大径円筒部４７とを有する。後蓋４の前端部、すなわち小径円筒部４５の前端部は、第２スリーブ３１のスペーサ５に接触している。   The rear lid 4 is formed in an annular shape, and the axle shaft S is inserted inside thereof. The rear lid 4 includes a small diameter cylindrical portion 45, a tapered portion 46 that increases in diameter toward the rear, and a large diameter cylindrical portion 47. The front end portion of the rear lid 4, that is, the front end portion of the small diameter cylindrical portion 45 is in contact with the spacer 5 of the second sleeve 31.

小径円筒部４５の外径は、後側の内輪７ｒにおける大つば１５の外径よりも小さく設定される。また、大径円筒部４７の外径は、後側の内輪７ｒにおける大つば１５の外径よりも大きく、外輪９の後端部における環状凹部１６ｒの径又はシールケース３３における取付部３９の外径とほぼ同じである。   The outer diameter of the small-diameter cylindrical portion 45 is set smaller than the outer diameter of the large collar 15 in the rear inner ring 7r. Further, the outer diameter of the large-diameter cylindrical portion 47 is larger than the outer diameter of the large brim 15 in the rear inner ring 7r, and the diameter of the annular recess 16r in the rear end portion of the outer ring 9 or the outside of the mounting portion 39 in the seal case 33. It is almost the same as the diameter.

以上説明した本実施形態に係る軸受装置１によれば、スペーサ５を後側の内輪７ｒの後端面と後蓋４の前端面との間に介在させることにより、この内輪７ｒと後蓋４の間のフレッティングによる摩耗を抑制できる。このスペーサ５は、第２スリーブ３１と一体に構成されていることから、スペーサ５の一部である第２スリーブ３１を後側の内輪７ｒの外周面に嵌合させることによって、このスペーサ５を内輪７ｒに位置決め及び固定されることになる。これにより、軸受装置１を車軸Ｓに組み付ける場合において、内輪７ｒを車軸Ｓに圧入する際にスティックスリップが生じたとしても、スペーサ５は内輪７ｒに固定されているため、振動によって倒れ込むということがない。   According to the bearing device 1 according to the present embodiment described above, the spacer 5 is interposed between the rear end surface of the rear inner ring 7r and the front end surface of the rear cover 4, so that the inner ring 7r and the rear cover 4 Wear due to fretting can be suppressed. Since the spacer 5 is configured integrally with the second sleeve 31, the spacer 5 is fitted by fitting the second sleeve 31 which is a part of the spacer 5 to the outer peripheral surface of the rear inner ring 7r. It is positioned and fixed to the inner ring 7r. As a result, when the bearing device 1 is assembled to the axle S, even if stick slip occurs when the inner ring 7r is press-fitted into the axle S, the spacer 5 is fixed to the inner ring 7r and thus falls down due to vibration. Absent.

したがって、軸受装置１を容易に効率良く車軸Ｓに組み付けることができるようになる。また、第２スリーブ３１を内輪７ｒの外周面に嵌合させたときに、スペーサ５が内輪７ｒの後端面に当接することにより、この第２スリーブ３１の位置決めも同時に行われる。したがって、本実施形態のように第２シール本体３２を第２スリーブ３１の外周面に摺接させる場合において、第２シール本体３２に対する第２スリーブ３１の位置決めを行う必要がなくなり、この観点からも車軸Ｓに対する軸受装置１の組み付け作業をより効率良く行うことができる。また、スペーサ５を第２スリーブ３１と一体に構成することにより、部品点数を低減することにもなり、これも組み付け作業性の向上に大きく寄与することになる。さらに、軸受装置１のメンテナンス時には、第２スリーブ３１とスペーサ５を同時に交換できることから、このメンテナンス作業をも容易に効率よく行うことができる。   Therefore, the bearing device 1 can be easily and efficiently assembled to the axle S. Further, when the second sleeve 31 is fitted to the outer peripheral surface of the inner ring 7r, the spacer 5 comes into contact with the rear end surface of the inner ring 7r, so that the positioning of the second sleeve 31 is also performed at the same time. Therefore, when the second seal body 32 is slidably contacted with the outer peripheral surface of the second sleeve 31 as in the present embodiment, it is not necessary to position the second sleeve 31 with respect to the second seal body 32. Assembling work of the bearing device 1 with respect to the axle shaft S can be performed more efficiently. Further, by forming the spacer 5 integrally with the second sleeve 31, the number of parts can be reduced, which also greatly contributes to an improvement in assembling workability. Furthermore, since the second sleeve 31 and the spacer 5 can be simultaneously replaced during the maintenance of the bearing device 1, this maintenance work can be easily and efficiently performed.

図３は、本発明に係る軸受装置１における他の例を示す。この例では、第２密封装置１２ｒにおけるシールケース３３の構成が図１及び図２の例とは異なる。この例におけるシールケース３３は、外輪９の後端部における環状凹部１６ｒに取り付けられる円筒状の取付部３９と、この取付部３９の一端から半径方向内方に突出する第１内側突出部４０ａと、この第１内側突出部４０ａから後方に突出する円筒部４８と、この円筒部４８の後端部から半径方向内方に突出する第２内側突出部４０ｂとを備える。   FIG. 3 shows another example of the bearing device 1 according to the present invention. In this example, the configuration of the seal case 33 in the second sealing device 12r is different from the example of FIGS. The seal case 33 in this example includes a cylindrical attachment portion 39 attached to the annular recess 16r at the rear end portion of the outer ring 9, and a first inner protrusion portion 40a protruding radially inward from one end of the attachment portion 39. A cylindrical portion 48 projecting backward from the first inner projecting portion 40a and a second inner projecting portion 40b projecting radially inward from the rear end portion of the cylindrical portion 48 are provided.

この例では、シールケース３３の第１内側突出部４０ａの突出端部を第２スリーブ３１における外周面に近接させることにより、その間にラビリンスシールが形成されている。また、第２内側突出部４０ｂの突出端部を後蓋４における小径円筒部４５の外周面に近接させることにより、その間にラビリンスシールが形成されている。   In this example, the labyrinth seal is formed between the projecting end portion of the first inner projecting portion 40a of the seal case 33 close to the outer peripheral surface of the second sleeve 31. Further, the protruding end portion of the second inner protruding portion 40 b is brought close to the outer peripheral surface of the small diameter cylindrical portion 45 in the rear lid 4, thereby forming a labyrinth seal therebetween.

図４及び図５は、本発明に係る軸受装置１における他の例を示す。これらの例では、第２密封装置１２ｒにおける第２スリーブ３１の構成が図１及び図２の例とは異なる。これらの例における第２スリーブ３１では、第２スリーブ３１の一端部（後端部）に、半径方向内方に突出するスペーサ５（内側突出部）が形成されるとともに、第２スリーブ３１の他端部（前端部）に、半径方向外方に突出する外側突出部４９が形成されている。   4 and 5 show another example of the bearing device 1 according to the present invention. In these examples, the configuration of the second sleeve 31 in the second sealing device 12r is different from the examples of FIGS. In the second sleeve 31 in these examples, one end portion (rear end portion) of the second sleeve 31 is formed with a spacer 5 (inner protruding portion) that protrudes inward in the radial direction. An outer protrusion 49 protruding outward in the radial direction is formed at the end (front end).

この外側突出部４９は、回転中に軸受内部のグリースが飛散して弾性シール３５に接触することを防止するためのものである。このため、外側突出部４９は、軸受内部側で、第２シール本体３２の弾性シール３５（本例では図示せず）よりも前側に位置している。また、外側突出部４９における半径方向外方への突出高さは、弾性シール３５のシールリップ３８の全体を覆うことが可能な高さに設定されることが望ましい。さらに、図５の例では、外側突出部４９の突出端部に、後方に向かって傾斜する傾斜部５０が設けられている。   The outer protrusion 49 is for preventing grease inside the bearing from scattering and contacting the elastic seal 35 during rotation. For this reason, the outer side protrusion part 49 is located in the bearing inner side and the front side rather than the elastic seal 35 (not shown in this example) of the 2nd seal main body 32. FIG. Further, it is desirable that the height of the outer protrusion 49 projecting outward in the radial direction is set to a height that can cover the entire seal lip 38 of the elastic seal 35. Furthermore, in the example of FIG. 5, an inclined portion 50 that is inclined rearward is provided at the protruding end portion of the outer protruding portion 49.

図６は、本発明に係る軸受装置１における他の例を示す。この例では、スペーサ５の一部である第２スリーブ３１の構成が図１及び図２の例とは異なる。この例では、第２スリーブ３１の内周面に、弾性体（例えばゴム製）によって構成される環状部材５１が設けられている。この例では、弾性変形可能な環状部材５１を第２スリーブ３１と内輪７ｒとの間に介在させることで、第２スリーブ３１に内輪７ｒが圧入されたときに、この環状部材５１の弾性変形によって内輪７ｒの変形による車軸Ｓとの局部的な摩耗が生じることを防止できる。   FIG. 6 shows another example of the bearing device 1 according to the present invention. In this example, the configuration of the second sleeve 31 that is a part of the spacer 5 is different from the example of FIGS. 1 and 2. In this example, an annular member 51 formed of an elastic body (for example, rubber) is provided on the inner peripheral surface of the second sleeve 31. In this example, an annular member 51 that is elastically deformable is interposed between the second sleeve 31 and the inner ring 7r, so that when the inner ring 7r is press-fitted into the second sleeve 31, the annular member 51 is elastically deformed. It is possible to prevent local wear on the axle S due to the deformation of the inner ring 7r.

なお、本発明に係る軸受装置１は、上記実施形態の構成に限定されるものではない。また、本発明に係る軸受装置１は、上記した作用効果に限定されるものでもない。本発明に係る軸受装置１は、本発明の要旨を逸脱しない範囲で種々の変更が可能である。   In addition, the bearing apparatus 1 which concerns on this invention is not limited to the structure of the said embodiment. Further, the bearing device 1 according to the present invention is not limited to the above-described effects. The bearing device 1 according to the present invention can be variously modified without departing from the gist of the present invention.

上記実施形態では、第２スリーブ３１とスペーサ５とを一体に構成した例を説明したが、これに限定されず、第１スリーブ２１についても第２スリーブ３２と同じ構成にしてもよい。すなわち、第１スリーブ２１とスペーサ（内側突出部）とを一体に構成し、この第１スリーブ２１を前側の内輪７ｆの外周面に嵌め込むとともに、スペーサ（内側突出部）を前側の内輪７ｆの前端面と前蓋３の当接部４３との間に介在させてもよい。   In the above-described embodiment, the example in which the second sleeve 31 and the spacer 5 are integrally configured has been described. However, the present invention is not limited to this, and the first sleeve 21 may have the same configuration as the second sleeve 32. That is, the first sleeve 21 and the spacer (inner protruding portion) are integrally formed, the first sleeve 21 is fitted into the outer peripheral surface of the front inner ring 7f, and the spacer (inner protruding portion) is fitted to the front inner ring 7f. You may interpose between the front-end surface and the contact part 43 of the front lid 3.

上記実施形態において、第２スリーブ３１の内周面に弾性体からなる環状部材５１を設けた例を示したが、これに限定されず、環状部材５１を第２スリーブ３１とは別体に構成し、この環状部材５１を内輪７ｒの外周面に取り付けた後に、第２スリーブ３１を環状部材５１の外周面に取り付けるようにしてもよい。また、環状部材５１を内輪７ｒの大つば１５の外周面に固着して一体化してもよい。   In the above embodiment, the example in which the annular member 51 made of an elastic body is provided on the inner peripheral surface of the second sleeve 31 is shown, but the present invention is not limited to this, and the annular member 51 is configured separately from the second sleeve 31. The second sleeve 31 may be attached to the outer peripheral surface of the annular member 51 after the annular member 51 is attached to the outer peripheral surface of the inner ring 7r. Further, the annular member 51 may be fixedly integrated with the outer peripheral surface of the large brim 15 of the inner ring 7r.

上記の実施形態では、転がり軸受として円すいころ軸受２を例示したが、これに限定されず、円筒ころ軸受その他の軸受についても本発明を適用できる。   In the above embodiment, the tapered roller bearing 2 is exemplified as the rolling bearing, but the present invention is not limited to this and can be applied to a cylindrical roller bearing and other bearings.

上記の実施形態では、環状に構成されたスペーサ５を例示したが、これに限らず、例えば、第２スリーブ３１の後端部の複数箇所から半径方向内方に突出する複数の内側突出部を形成し、これらをスペーサ５としてもよい。   In the above-described embodiment, the annularly configured spacer 5 is exemplified. However, the present invention is not limited to this, and for example, a plurality of inner protrusions that protrude radially inward from a plurality of locations at the rear end of the second sleeve 31 are provided. These may be formed and used as the spacer 5.

１ 軸受装置
２ 軸受（円すいころ軸受）
３ 前蓋
４ 後蓋
５ スペーサ
７ 内輪
９ 外輪
１０ 転動体（円すいころ）
１１ 保持器
１２ 密封装置
３１ 第２スリーブ
３２ シール本体
４９ 外側突出部
５１ 環状部材
Ｓ 車軸 1 Bearing device 2 Bearing (tapered roller bearing)
3 Front lid 4 Rear lid 5 Spacer 7 Inner ring 9 Outer ring 10 Rolling element (tapered roller)
11 Cage 12 Sealing device 31 Second sleeve 32 Seal body 49 Outer protrusion 51 Annular member S Axle

Claims (7)

外周面に軌道を有する内輪と、内周面に軌道を有する外輪と、前記内輪の前記軌道と前記外輪の前記軌道との間で転動可能に保持される転動体とを有する軸受と、
前記軸受を車軸に固定するための前蓋及び後蓋と、
前記内輪と前記後蓋との間に介在するスペーサと、を備え、
前記スペーサの一部が前記内輪の外周面に嵌合する鉄道車両用軸受装置。 A bearing having an inner ring having a raceway on an outer peripheral surface, an outer ring having a raceway on an inner peripheral surface, and a rolling element held to roll between the raceway of the inner ring and the raceway of the outer ring;
A front lid and a rear lid for fixing the bearing to the axle;
A spacer interposed between the inner ring and the rear lid,
A railway vehicle bearing device in which a part of the spacer is fitted to the outer peripheral surface of the inner ring. 前記スペーサの一部は、前記内輪の外周面に嵌合するスリーブとして構成され、
前記軸受は、前記外輪の前記内周面に取り付けられるとともに、前記スペーサの前記スリーブに摺接するシール本体を備える請求項１に記載の鉄道車両用軸受装置。 A part of the spacer is configured as a sleeve fitted to the outer peripheral surface of the inner ring,
The railway vehicle bearing device according to claim 1, wherein the bearing includes a seal body that is attached to the inner peripheral surface of the outer ring and that is in sliding contact with the sleeve of the spacer. 前記スペーサは、前記スリーブから半径方向内方に突出するとともに前記内輪の端部と前記後蓋の端面の双方に接触する内側突出部を備える請求項２に記載の鉄道車両用軸受装置。   3. The railway vehicle bearing device according to claim 2, wherein the spacer includes an inner protruding portion that protrudes radially inward from the sleeve and contacts both an end portion of the inner ring and an end surface of the rear lid. 前記スリーブから半径方向外方に突出するとともに、軸受内部側で前記シール本体を覆う外側突出部を備える請求項２又は３に記載の鉄道車両用軸受装置。   The railway vehicle bearing device according to claim 2, further comprising an outer protrusion that protrudes radially outward from the sleeve and covers the seal body on an inner side of the bearing. 前記スペーサは、鋼材又は黄銅により構成される請求項１から４のいずれか１項に記載の鉄道車両用軸受装置。   The railcar bearing device according to any one of claims 1 to 4, wherein the spacer is made of steel or brass. 前記スリーブの内周面と前記内輪の前記外周面との間に弾性体による環状部材が介在する請求項２から５のいずれか１項に記載の鉄道車両用軸受装置。   The railway vehicle bearing device according to any one of claims 2 to 5, wherein an annular member made of an elastic body is interposed between an inner peripheral surface of the sleeve and the outer peripheral surface of the inner ring. 前記スペーサにダイヤモンドライクカーボンによる被膜が形成される請求項２から６のいずれか１項に記載の鉄道車両用軸受装置。
The railway vehicle bearing device according to any one of claims 2 to 6, wherein a coating of diamond-like carbon is formed on the spacer.
JP2015019419A 2015-02-03 2015-02-03 Bearing device for railway vehicle Pending JP2016142364A (en)

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RU196700U1 (en) * 2019-12-09 2020-03-12 Акционерное общество "ЕПК Саратов" BEAM BEARING ASSEMBLY

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