JP2005147185A - Double row rolling bearing - Google Patents

Double row rolling bearing Download PDF

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Publication number
JP2005147185A
JP2005147185A JP2003381927A JP2003381927A JP2005147185A JP 2005147185 A JP2005147185 A JP 2005147185A JP 2003381927 A JP2003381927 A JP 2003381927A JP 2003381927 A JP2003381927 A JP 2003381927A JP 2005147185 A JP2005147185 A JP 2005147185A
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Prior art keywords
spacer
rolling bearing
lines
axle
ring
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Japanese (ja)
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Kenji Iwaguchi
健二 岩口
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Nachi Fujikoshi Corp
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Nachi Fujikoshi Corp
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Priority to JP2003381927A priority Critical patent/JP2005147185A/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

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  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To prevent damage to a small diameter portion of an axle around both ends of inner rings of a double row rolling bearing. <P>SOLUTION: The double row rolling bearing comprises the plurality of inner rings 2, 3, a rolling body 4, an outer ring 6, and a spacer 5 held between the plurality of inner rings. The axially sectional shape of an inner diameter hole 15 of the spacer is a combination of one or more curves, lines and lines, lines and curves, or curves and curves. Connection parts between the curves or between the lines have no sharp portions. All radii R of curvature of the connection parts between the curves and between the lines are each 5 mm or more. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明は、例えば鉄道車両用車軸軸受に使用される内輪間座を有する複列ころがり軸受に関し、特に内輪間座の内径穴の軸方向断面形状の改良に関する。   The present invention relates to a double-row rolling bearing having an inner ring spacer used for, for example, an axle bearing for a railway vehicle, and more particularly to improvement of an axial sectional shape of an inner diameter hole of the inner ring spacer.

例えば、図５に示すように、鉄道車両用軸受装置３１は、図示しない車輪がしまりばめで嵌挿固着された大径部３２、先細りの肩部３３、テーパころ４を有するテーパころがり軸受２１の二個の内輪２，３内径２ａ，３ａがしまりばめで嵌合される小径部３４が順次形成され、小径部端である車軸端３５にねじ部３６が設けられている。先細りの肩部３３とねじ部３６に螺合された締め付けリング３７間に、車軸端側シールリング３８、テーパころがり軸受内輪２、間座２５、もう一方の内輪３、大径部側シールリング３９が順次挟持固定されている。シールリング３８，３９はテーパころがり軸受２１の外輪６に設けられたシール部材４２，４３のシール部４４，４５と摺接し、テーパころがり軸受２１への外部からの塵埃等の侵入を防止するためのシール機構とされている。締め付けリング３７には締め付けリングの回り止め４０が取り付けられ、さらにキャップ４１が設けられている。テーパころがり軸受２１は前述した外輪６と、二個の内輪２，３と、二個の内輪間に挟持された間座２５と、内外輪間を転動する二列のテーパころ（転動体）４と、テーパころを保持する保持器７から構成されている。かかる複列ころがり軸受２１においては、軸受寿命を延ばし、運転中の騒音や、振動を低減し、性能を確保するために内部隙間を調整する必要がある。このため、リング状の間座２５を内輪２，３間に設けて、内輪間の軸方向隙間を調整するようにされている。   For example, as shown in FIG. 5, the railway vehicle bearing device 31 includes a tapered roller bearing 21 having a large-diameter portion 32, a tapered shoulder portion 33, and a tapered roller 4. A small-diameter portion 34 in which the two inner rings 2 and 3 inner diameters 2a and 3a are fitted by fit is formed sequentially, and a screw portion 36 is provided at an axle end 35 which is a small-diameter portion end. Between the tapered shoulder portion 33 and the tightening ring 37 screwed into the screw portion 36, the axle end side seal ring 38, the tapered roller bearing inner ring 2, the spacer 25, the other inner ring 3, and the large diameter side seal ring 39. Are clamped and fixed sequentially. The seal rings 38 and 39 are in sliding contact with the seal portions 44 and 45 of the seal members 42 and 43 provided on the outer ring 6 of the tapered roller bearing 21 to prevent entry of dust and the like from the outside into the tapered roller bearing 21. It is a sealing mechanism. A fastening ring detent 40 is attached to the fastening ring 37, and a cap 41 is further provided. The tapered roller bearing 21 includes the outer ring 6, the two inner rings 2 and 3, the spacer 25 sandwiched between the two inner rings, and two rows of tapered rollers (rolling elements) that roll between the inner and outer rings. 4 and a cage 7 for holding tapered rollers. In such a double-row rolling bearing 21, it is necessary to adjust the internal clearance in order to extend the bearing life, reduce noise and vibration during operation, and ensure performance. For this reason, a ring-shaped spacer 25 is provided between the inner rings 2 and 3 to adjust the axial clearance between the inner rings.

かかる鉄道車両用軸受装置３１は、近年、コンパクト化やメンテナンスフリー化により、荷重条件が厳しくなっており、種々の場所でフレッチング摩耗が発生し、その対策がとられている。例えば、従来の内輪間座近傍の拡大断面図である図４に示すように、内輪内径２ａ，３ａ端の面取り部２ｃ、３ｃ近傍での車軸の小径部３４のフレッチング摩耗の発生を防止するために、内輪内径面と面取り部の接続部をラップ等により滑らかにしてエッジ応力の低減を図っている。さらに、特許文献１においては、内輪内径面の面取り部の形状を面取り角にして７°以下、内輪内径面と面取り部との交点を曲率半径５ｍｍ以上の円弧とし、さらに面粗さをＲｚ＝６．３以下としたものが開示されている。また、特許文献２のものにおいては、内輪２，３と間座２５の当たり面２５ｂにダイヤモンドライクカーボン膜をコーティングして間座と内輪との間２５ｂに発生するフレッチング摩耗の発生を防止している。
特許第３３５６５４０号公報 特許請求の範囲 図１ 特開２００３−３０１８４７号公報 In recent years, such a railway vehicle bearing device 31 has been subjected to severe load conditions due to downsizing and maintenance-free operation, and fretting wear occurs in various places, and countermeasures are taken. For example, as shown in FIG. 4 which is an enlarged cross-sectional view in the vicinity of a conventional inner ring spacer, in order to prevent the occurrence of fretting wear of the small-diameter portion 34 of the axle near the chamfered portions 2c and 3c at the ends of the inner ring inner diameters 2a and 3a. In addition, the connection between the inner ring inner diameter surface and the chamfered portion is smoothed by wrapping or the like to reduce the edge stress. Furthermore, in Patent Document 1, the shape of the chamfered portion of the inner ring inner diameter surface is a chamfer angle of 7 ° or less, the intersection of the inner ring inner diameter surface and the chamfered portion is an arc having a curvature radius of 5 mm or more, and the surface roughness is Rz = What is 6.3 or less is disclosed. Further, in Patent Document 2, a diamond-like carbon film is coated on the contact surfaces 25b of the inner rings 2, 3 and the spacer 25 to prevent the occurrence of fretting wear that occurs between the spacer and the inner ring 25b. Yes.
Japanese Patent No. 3356540 Patent Claims FIG. JP 2003-301847 A

しかし、内輪内径２ａ，３ａ端付近の車軸の小径部３４側に依然として、フレッチング摩耗や、特に傷５１が発生しており、その対策が望まれていた。一方、内輪２，３が車軸の小径部３４にしまりばめで嵌合されているのに対し、内輪２，３に挟持された間座２５の内径２５ａは車軸の小径部３４の外径３４ａとは片側で数十μｍから数ｍｍ程度の微少隙間１１を有するように設計されており、さらに、内輪間座２５の内径面形状は、内径面２５の両端面に１Ｃ程度の平面取り、又は１．５Ｒ程度の曲面取り２５ｃが施こされており、フレッチング摩耗や傷の原因とは認められていなかった。   However, fretting wear and particularly scratches 51 are still generated on the side of the small-diameter portion 34 of the axle near the ends of the inner ring inner diameters 2a and 3a. On the other hand, the inner rings 2 and 3 are fitted to the small diameter portion 34 of the axle with a fit, whereas the inner diameter 25a of the spacer 25 sandwiched between the inner rings 2 and 3 is the same as the outer diameter 34a of the small diameter portion 34 of the axle. Is designed to have a minute gap 11 of about several tens of μm to several mm on one side. Further, the inner ring spacer 25 has an inner surface shape of about 1 C on both end surfaces of the inner surface 25, or 1 A curved surface capping of about 5R was applied, and it was not recognized as a cause of fretting wear or scratches.

本発明の課題は、かかる軸受装置に発生する傷の原因をつきとめ、両内輪端付近に発生する車軸の小径部の傷の発生を防ぐ複列ころがり軸受を提供することである。   An object of the present invention is to provide a double-row rolling bearing that can determine the cause of scratches that occur in such a bearing device and prevent the occurrence of scratches in the small-diameter portions of the axles that occur near both inner ring ends.

本発明者は、かかるフレッチング摩耗や傷を詳細に調べ研究した結果、図４を参照して説明すると、間座２５が車軸の小径部３４と隙間１１を有しているにもかかわらず、使用上車軸がたわんだり、間座が半径方向に移動したりして、車軸の小径部と間座とが接触して傷を発生していることをつきとめた。さらに、この傷は、間座２５の内径部の直線部２３ａと面取り２５ｃとの接続部２６近傍に発生しており、この直線部と面取り部とが作る鋭部が車軸の小径部３４に押し当てられ、小径部に細い線状の傷５１が発生するということを知得した。さらには、この傷を起点にフレッチング摩耗が発生することも考えられる。   As a result of detailed investigation and research on such fretting wear and scratches, the present inventor has described that with reference to FIG. 4, although the spacer 25 has the small diameter portion 34 of the axle and the gap 11, it is used. It was found that the upper axle was bent and the spacer was moved in the radial direction, and the small diameter portion of the axle and the spacer contacted each other to cause scratches. Further, this scratch is generated in the vicinity of the connecting portion 26 between the linear portion 23a of the inner diameter portion of the spacer 25 and the chamfer 25c, and the sharp portion formed by this linear portion and the chamfered portion pushes the small diameter portion 34 of the axle. It was found that a thin line-shaped scratch 51 was generated in the small diameter portion. Furthermore, fretting wear may occur from this scratch.

この知得により、本発明においては、少なくとも複数の内輪と、前記内輪の軌道面を転動するようにされた転動体と、前記転動体を介して前記複数の内輪に対応する軌道面を有する外輪と、前記複数の内輪間に挟持された間座と、を有する複列ころがり軸受において、前記間座の内径穴の軸方向断面形状が曲線、又は直線と直線、又は直線と曲線、又は曲線と曲線の単数又は複数の組合せであって、前記曲線、又は前記各線を結ぶ接続部に鋭部がない複列ころがり軸受を提供することにより前述した課題を解決した。   With this knowledge, the present invention has at least a plurality of inner rings, a rolling element that rolls on the raceway surface of the inner ring, and a raceway surface that corresponds to the plurality of inner rings via the rolling element. In a double row rolling bearing having an outer ring and a spacer sandwiched between the plurality of inner rings, the axial sectional shape of the inner diameter hole of the spacer is a curve, or a straight line and a straight line, or a straight line and a curve, or a curved line The above-mentioned problems have been solved by providing a double-row rolling bearing that is a single or a combination of a plurality of curves and that has no sharp portions at the connecting portions connecting the curves or the lines.

即ち、設計寸法上は車軸と隙間を有する間座であっても、前述した内輪内径端の面取りと同様に、間座の内径穴の軸方向断面形状を曲線、又は直線と直線、又は直線と曲線、又は曲線と曲線の単数又は複数の組合せの、曲線及び各線を結ぶ接続部を鋭部とさせないようにしたので、車軸のたわみや、間座の半径方向の移動等による車軸の小径部と間座内径の鋭部との接触がなくなるので、傷の発生が減少、又はない。   In other words, even in the case of a spacer having a gap between the axle and the design dimension, the axial cross-sectional shape of the inner diameter bore of the spacer is a curve, a straight line and a straight line, or a straight line, similar to the chamfering of the inner ring inner diameter end described above. Since the connection part connecting the curve and each line of the curve or a combination of the curve and the curve is made not to be a sharp part, the small diameter part of the axle due to the deflection of the axle, the movement of the spacer in the radial direction, etc. Since there is no contact with the sharp part of the inner diameter of the spacer, the occurrence of scratches is reduced or absent.

より好ましくは、請求項２に記載のように、前記曲線及び各線を結ぶ接続部の全ての曲率半径が５ｍｍ以上にされている複列ころがり軸受とする。この値は、フレッチング摩耗の場合ではあるが、前述した従来の内輪内径端の面取りで実績があり、また、設計上車軸の小径部と隙間を有する間座においては、十分な値である。   More preferably, as described in claim 2, a double row rolling bearing in which all the radii of curvature of the connecting portions connecting the curved lines and the respective lines are 5 mm or more. Although this is a case of fretting wear, this value has been proven in the conventional chamfering of the inner ring inner diameter end described above, and is sufficient for a spacer having a small diameter portion and a gap in the design.

本発明においては、設計上車軸の小径部とは隙間を有する間座でありながら、使用にあたっては間座の内径穴と内径穴面取り部との接続部が車軸と干渉するという点に着目して、曲線部及び曲線部と直線部等の接続部の鋭部を取り除き、車軸のたわみや、間座の半径方向の移動等による車軸の小径部と間座内径の鋭部との接触をなくしたので、傷の発生を抑えるという効果を奏するものとなった。さらにこの傷を起点とするフレッチング摩耗の発生も抑えられる。また、接続部や曲面の曲率半径を５ｍｍ以上とすれば、簡単に、より確実に傷の発生をおさえることができる。   In the present invention, the small-diameter portion of the axle is designed to be a spacer having a gap, but in use, the connection between the inner-diameter hole of the spacer and the inner-hole chamfered portion interferes with the axle. The sharp part of the connecting part such as the curved part and the curved part and the straight part is removed, and the contact between the small diameter part of the axle and the sharp part of the spacer inner diameter due to the deflection of the axle or the movement of the spacer in the radial direction is eliminated. Therefore, the effect of suppressing the occurrence of scratches was achieved. Further, the occurrence of fretting wear starting from this scratch can be suppressed. Moreover, if the radius of curvature of the connecting portion or the curved surface is set to 5 mm or more, the generation of scratches can be suppressed easily and more reliably.

本発明の実施の形態の一例を、図を参照して説明する。図１は本発明の実施の形態を示す内輪間座を有する密封複式円錐ころ軸受及び車軸の取付部分の断面図、図２は本発明の実施の形態を示す内輪間座近傍の拡大断面図である。なお、前述した従来例である図４、５と同様の部分については相互に同じ符号を付し説明の一部を省略する。図１に示すように、本発明密封複列ころがり軸受１は、二個の内輪２，３に挟持された間座５を有しており、二個の内輪の内径穴２ａ，３ａが車軸の小径部３４にしまりばめで嵌着され、シールリングを３７，３９介して締め付けリング３７と先細りの肩部３３により挟持固定されている。内輪２，３は円錐面の軌道面８，８を有し、軌道面の小径側に小鍔９、大径側に大鍔１０が設けられており、軌道面を転動する複数個のテーパころ４、４の軸方向移動を規制している。内輪２，３は互いに小鍔９側を対向させて小鍔端９ａ，９ａ間に間座５が配設される。内輪２，３の外側に対応してテーパころ４，４が転動するテーパ穴状の軌道面１２，１２を有する外輪６が設けられ、内外輪がテーパころを介して互いに回転可能にされている。また、テーパころの間隔を適正にするための保持器７，７が設けられている。外輪６は一体とされ、中央部に潤滑口１３が設けられており、この潤滑口よりグリースを充填する等して転動体４と内外輪軌道面８，１２、保持器７をグリース潤滑させる。   An example of an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view of a sealed double tapered roller bearing having an inner ring spacer and an axle mounting portion showing an embodiment of the present invention, and FIG. 2 is an enlarged sectional view in the vicinity of the inner ring spacer showing an embodiment of the present invention. is there. Parts similar to those of the conventional example shown in FIGS. 4 and 5 are denoted by the same reference numerals, and a part of the description is omitted. As shown in FIG. 1, the sealed double-row rolling bearing 1 of the present invention has a spacer 5 sandwiched between two inner rings 2 and 3, and the inner diameter holes 2a and 3a of the two inner rings are the axles. The small-diameter portion 34 is fitted with an interference fit, and the seal ring 37 is sandwiched and fixed by a tightening ring 37 and a tapered shoulder portion 33 through 39. The inner rings 2 and 3 have conical raceway surfaces 8 and 8, and are provided with a small flange 9 on the small diameter side of the track surface and a large flange 10 on the large diameter side, and a plurality of tapers that roll on the track surface. The movement of the rollers 4 and 4 in the axial direction is restricted. The inner rings 2 and 3 are provided with a spacer 5 between the small edge ends 9a and 9a with the small edge 9 facing each other. Corresponding to the outer sides of the inner rings 2 and 3, an outer ring 6 having tapered raceway surfaces 12 and 12 on which the tapered rollers 4 and 4 roll is provided, and the inner and outer rings can be rotated with each other via the tapered rollers. Yes. Moreover, the holder | retainers 7 and 7 for making the space | interval of a taper roller appropriate are provided. The outer ring 6 is integrated, and a lubrication port 13 is provided in the center. The rolling element 4, the inner and outer ring raceway surfaces 8 and 12, and the cage 7 are grease-lubricated by filling grease through the lubrication port.

間座５を挟んで内輪２，３を互いに締め付けリング３７と先細りの肩部３３とで挟持固定することにより、テーパころ７、内外輪２，３，６間の内部隙間を変化させることができ、間座５の幅寸法Ｌを調整することにより内部隙間を調整できる。外輪６の外周６ａは図示しない台車の軸箱に取り付けられ、車輪が回転可能にされている。図２に示すように、この間座５の内径５ａは車軸小径部３４の内径３４ａ、内輪内径２ａ，３ａより大きくされ車軸の小径部とは、片側で数十μｍから数ｍｍの隙間１１が設けられている。本発明においては、特に、間座５の軸方向断面の内径穴１５の形状は円弧、いわゆるフルクラウニングとされている。より具体的な寸法例としては、内輪内径（車軸の小径部）ｄがφ１２０ｍｍの場合で、間座外径Ｄはφ１３８ｍｍ、幅Ｌは１０ｍｍ程度であり、内径穴１５の円弧の曲率半径Ｒは１０ｍｍである。なお、間座５の外径側の面取り５ｄの曲率半径は１．５ｍｍである。また、間座内径５ａと車軸の小径部３４との隙間１１は片側で０．１ｍｍである。一方、前述した図４に示す従来の間座２５においては、同様に内輪内径ｄがφ１２０ｍｍの場合で、間座外径Ｄはφ１３８ｍｍ、幅Ｌは１０ｍｍ、内径２５ａと車軸の小径部３４との隙間１１は片側で０．１ｍｍであり、特に、従来のものは、内径及び外径側の面取り２５ｃ，２５ｄは同じ形状にされており、その曲率半径は１．５ｍｍである。   By sandwiching and fixing the inner rings 2 and 3 with the fastening ring 37 and the tapered shoulder 33 with the spacer 5 interposed therebetween, the internal gap between the tapered roller 7 and the inner and outer rings 2, 3 and 6 can be changed. The internal gap can be adjusted by adjusting the width dimension L of the spacer 5. An outer periphery 6a of the outer ring 6 is attached to a bogie axle box (not shown) so that the wheel can rotate. As shown in FIG. 2, the inner diameter 5a of the spacer 5 is larger than the inner diameter 34a of the axle small diameter portion 34 and the inner ring inner diameters 2a and 3a, and a gap 11 of several tens μm to several mm is provided on one side of the small diameter portion of the axle. It has been. In the present invention, in particular, the shape of the inner diameter hole 15 in the axial section of the spacer 5 is an arc, so-called full crowning. As a more specific dimension example, the inner ring inner diameter (the small diameter portion of the axle) d is φ120 mm, the spacer outer diameter D is φ138 mm, the width L is about 10 mm, and the radius of curvature R of the arc of the inner diameter hole 15 is 10 mm. The curvature radius of the chamfer 5d on the outer diameter side of the spacer 5 is 1.5 mm. Further, the gap 11 between the spacer inner diameter 5a and the small diameter portion 34 of the axle is 0.1 mm on one side. On the other hand, in the conventional spacer 25 shown in FIG. 4 described above, when the inner ring inner diameter d is φ120 mm, the spacer outer diameter D is φ138 mm, the width L is 10 mm, the inner diameter 25a and the small diameter portion 34 of the axle. The gap 11 is 0.1 mm on one side. In particular, in the conventional one, the chamfers 25c and 25d on the inner and outer diameter sides have the same shape, and the radius of curvature is 1.5 mm.

かかる図２及び図４のものについて、使用後の傷の状態を調査した結果、図４に示す従来のものは、間座内径２５ａ側の面取り部２５ｃと内径直線部２５ａとの接続部２６に相当する車輪の小径部３４外周３４ａに傷５１が発生したのに対し、図２に示す本発明の間座を使用したものは係る傷の発生がなかった。また、図３は本発明の他の実施例を示す間座の軸方向断面図であり、直線と曲線とを結んだものである。図３に示すように、間座５′の内径穴１５′の中央部近傍が直線１６とされ、直線を接線として両側に曲線部１７が形成されており、曲線部の曲率半径Ｒ′は５ｍｍである。その他は前述した図２のものと同様である。この場合も曲線１７と直線１６との接続部１８での傷の発生はなかった。   As a result of investigating the state of scratches after use of these FIG. 2 and FIG. 4, the conventional one shown in FIG. 4 has a connection portion 26 between the chamfered portion 25 c on the spacer inner diameter 25 a side and the inner diameter linear portion 25 a. The scratches 51 occurred on the outer periphery 34a of the corresponding small-diameter portion 34 of the wheel, whereas those using the spacer of the present invention shown in FIG. 2 did not cause such scratches. FIG. 3 is a sectional view in the axial direction of a spacer showing another embodiment of the present invention, which connects a straight line and a curved line. As shown in FIG. 3, the vicinity of the center portion of the inner diameter hole 15 'of the spacer 5' is a straight line 16, curved portions 17 are formed on both sides with the straight line as a tangent, and the curvature radius R 'of the curved portion is 5 mm. It is. Others are the same as those of FIG. Also in this case, there was no scratch at the connecting portion 18 between the curve 17 and the straight line 16.

このように、従来の内輪間座に対し、本発明においては、内輪間座の内径面形状が曲線、又は直線部と直線部、又は直線部と曲線部、さらには曲線部と曲線部との接続部の鋭部や曲線を例えば曲率半径で５ｍｍ以上とする簡単なことにより、鋭部が取り除かれ、車軸の小径部への傷は発生しなくなる。   Thus, in contrast to the conventional inner ring spacer, in the present invention, the inner surface shape of the inner ring spacer is a curve, or a straight part and a straight part, or a straight part and a curved part, and further, a curved part and a curved part. By making the sharp part and the curve of the connecting part as simple as, for example, a radius of curvature of 5 mm or more, the sharp part is removed, and the small diameter part of the axle is not damaged.

本発明の実施の形態を示す内輪間座を有する密封複式円錐ころ軸受及び車軸の取付部分の断面図である。1 is a cross-sectional view of a sealed double tapered roller bearing having an inner ring spacer and an axle mounting portion according to an embodiment of the present invention. 本発明の実施の形態を示す内輪間座近傍の拡大断面図である。It is an expanded sectional view near the inner ring spacer showing an embodiment of the present invention. 本発明の他の実施の形態を示す内輪間座近傍の拡大断面図である。It is an expanded sectional view of the inner ring spacer vicinity which shows other embodiment of this invention. 従来の内輪間座近傍の拡大断面図である。It is an expanded sectional view near the conventional inner ring spacer. 従来の内輪間座を有する密封複式円錐ころ軸受及び車軸の取付部分の断面図である。It is sectional drawing of the installation part of the sealed double tapered roller bearing which has the conventional inner ring | wheel spacer, and an axle.

符号の説明Explanation of symbols

１ 複列ころがり軸受
２、３ 内輪
４ 転動体
５、５′ 間座
６ 外輪
８ 内輪の軌道面
１２ 外輪の軌道面
１５、１５′ 間座の内径穴
１８ 接続部
Ｒ、Ｒ′曲線及び各線を結ぶ接続部の曲率半径
DESCRIPTION OF SYMBOLS 1 Double row rolling bearing 2, 3 Inner ring 4 Rolling element 5, 5 'Spacer 6 Outer ring 8 Inner ring raceway surface 12 Outer ring raceway surface 15, 15' Spacer inner diameter hole 18 Connection part R, R 'curve and each line Curvature radius of connecting part

Claims (2)

少なくとも複数の内輪と、前記内輪の軌道面を転動するようにされた転動体と、前記転動体を介して前記複数の内輪に対応する軌道面を有する外輪と、前記複数の内輪間に挟持された間座と、を有する複列ころがり軸受において、前記間座の内径穴の軸方向断面形状が曲線、又は直線と直線、又は直線と曲線、又は曲線と曲線の単数又は複数の組合せであって、前記曲線、又は前記各線を結ぶ接続部に鋭部がないことを特徴とする複列ころがり軸受。   At least a plurality of inner rings, a rolling element configured to roll on a raceway surface of the inner ring, an outer ring having a raceway surface corresponding to the plurality of inner rings via the rolling element, and sandwiched between the plurality of inner rings In the double row rolling bearing having the spacer, the axial sectional shape of the inner diameter hole of the spacer is a curve, a straight line and a straight line, or a straight line and a curve, or a combination of a curve and a curve. The double row rolling bearing is characterized in that the curved line or the connecting part connecting the lines does not have a sharp part. 前記曲線及び各線を結ぶ接続部の全ての曲率半径が５ｍｍ以上にされていることを特徴とする請求項１記載の複列ころがり軸受。
2. The double row rolling bearing according to claim 1, wherein the curvature radii of all the connecting portions connecting the curved lines and the respective lines are 5 mm or more.
JP2003381927A 2003-11-12 2003-11-12 Double row rolling bearing Pending JP2005147185A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003381927A JP2005147185A (en) 2003-11-12 2003-11-12 Double row rolling bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2003381927A JP2005147185A (en) 2003-11-12 2003-11-12 Double row rolling bearing

Publications (1)

Publication Number Publication Date
JP2005147185A true JP2005147185A (en) 2005-06-09

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ID=34691125

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2003381927A Pending JP2005147185A (en) 2003-11-12 2003-11-12 Double row rolling bearing

Country Status (1)

Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007263194A (en) * 2006-03-28 2007-10-11 Ntn Corp Rocking bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007263194A (en) * 2006-03-28 2007-10-11 Ntn Corp Rocking bearing
JP4536675B2 (en) * 2006-03-28 2010-09-01 Ｎｔｎ株式会社 Swing bearing

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