JP2005325867A - Bearing for railroad car - Google Patents

Bearing for railroad car Download PDF

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JP2005325867A
JP2005325867A JP2004142550A JP2004142550A JP2005325867A JP 2005325867 A JP2005325867 A JP 2005325867A JP 2004142550 A JP2004142550 A JP 2004142550A JP 2004142550 A JP2004142550 A JP 2004142550A JP 2005325867 A JP2005325867 A JP 2005325867A
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Prior art keywords
bearing
ring
annular spacer
axle
inner ring
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JP2004142550A
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Japanese (ja)
Inventor
Shoji Matsuoka
章二 松岡
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2004142550A priority Critical patent/JP2005325867A/en
Publication of JP2005325867A publication Critical patent/JP2005325867A/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C35/063—Fixing them on the shaft
    • 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 provide a bearing for a railroad car capable of preventing leakage of grease even at a high speed rotation range. <P>SOLUTION: The bearing for a railroad car is provided with an inner ring 4 mounted on an axle, an outer ring 5 arranged on an outer periphery of the inner ring 4 by interposing a plurality of rolling bodies 6, ring members 2 and 3 mounted on the axle and regulating an axial position of the inner ring 4 against the axle, and a circular spacer 20 arranged between both breadth faces of the inner ring 4 and the ring members 2 and 3. the circular spacer 20 is made of a different material such as a brass, and its end at the outer diameter is extended outward in a radial direction. A labyrinth gap is formed between the end at the outer diameter of the circular spacer 20 and the bore surface of the outer seal case 12. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、発熱とフレッティング摩耗を抑制しつつ、密封性、耐水性および耐ダスト性を向上させた鉄道車両用軸受に関する。  The present invention relates to a railway vehicle bearing having improved sealing performance, water resistance and dust resistance while suppressing heat generation and fretting wear.

鉄道車両では密封型車軸軸受（円錐ころ軸受または円筒ころ軸受）が使用される。円錐ころ軸受を使用した車軸軸受を図４に示す。軸受１の内輪４の両側に各々接して、油切り２および後ろ蓋３が設けられる。車軸には鉄道車両の荷重によって大きな曲げモーメントが作用し、内輪４と油切り２との接触面ａ、および、内輪４と後ろ蓋３との接触面ｂには、繰返し応力が発生する。とりわけ、後者の接触面ｂにはより大きな繰返し応力が発生する。油切り２および後ろ蓋３は、焼ならししただけの炭素鋼を使用することが多い。このため、接触面ａ，ｂは前記繰返し応力により短期間のうちに摩耗（フレッティング摩耗）しやすい。摩耗による軸受寿命短縮を避けるため接触面ａ，ｂに銅合金などの軟質金属を挟み込むこともあるが、摩耗粉自体の発生は避けられない。摩耗粉が軸受１内の潤滑剤に混入すると、潤滑剤の劣化の原因となる。  Sealed axle bearings (conical roller bearings or cylindrical roller bearings) are used in railway vehicles. An axle bearing using a tapered roller bearing is shown in FIG. An oil drain 2 and a rear lid 3 are provided in contact with both sides of the inner ring 4 of the bearing 1. A large bending moment acts on the axle due to the load of the railway vehicle, and repeated stress is generated on the contact surface a between the inner ring 4 and the oil drain 2 and the contact surface b between the inner ring 4 and the rear lid 3. In particular, a larger repetitive stress is generated on the latter contact surface b. The oil drainer 2 and the rear lid 3 are often made of just normalized carbon steel. For this reason, the contact surfaces a and b are likely to wear (fretting wear) in a short period of time due to the repeated stress. In order to avoid shortening the bearing life due to wear, a soft metal such as a copper alloy may be sandwiched between the contact surfaces a and b, but the generation of wear powder is inevitable. When the wear powder is mixed into the lubricant in the bearing 1, it causes deterioration of the lubricant.

摩耗粉の軸受１内への侵入防止対策として、図５に示すように、内輪４と後ろ蓋３との接触面ｂの外径部に円環状の溝５を形成し、この溝５内に円環状の弾性体１５を嵌め込んだものが提案されている（特許文献１参照）。なお、図示はしないが、内輪４と油切り２との接触面ａにも同様に弾性体１５を嵌め込む。この構成によると、接触面ａ，ｂで発生した摩耗粉が、外径方向に移動しようとしても弾性体１５によって阻止される。そのため、軸受１内に摩耗粉が混入することが防止できる。弾性体１５は、フレッティング摩耗を防止するリング状の異材プレートと一体にした弾性体付き環状スペーサ２０として装着する場合もある。  As a measure for preventing wear powder from entering the bearing 1, as shown in FIG. 5, an annular groove 5 is formed in the outer diameter portion of the contact surface b between the inner ring 4 and the rear lid 3. One in which an annular elastic body 15 is fitted has been proposed (see Patent Document 1). Although not shown, the elastic body 15 is similarly fitted to the contact surface a between the inner ring 4 and the oil drain 2. According to this configuration, the abrasion powder generated on the contact surfaces a and b is blocked by the elastic body 15 even if it tries to move in the outer diameter direction. Therefore, it is possible to prevent wear powder from being mixed into the bearing 1. The elastic body 15 may be mounted as an annular spacer 20 with an elastic body integrated with a ring-shaped dissimilar material plate that prevents fretting wear.

内輪４と外輪５との間には、内外輪の軌道面を潤滑するためにグリースが充填される。内外輪間の端部は、グリースが漏れ出ないように、また外部からのダストが内外輪間に侵入しないように、オイルシール９，１１が配設される。このオイルシール９，１１は、一方オイルシール１１について図５に示すように、外輪５の内径に基端部が嵌合し先端部が前記リング部材（後ろ蓋３）側に延在した外側シールケース１２と、リング部材（後ろ蓋３）の外径面に嵌合すると共に外側シールケース１２の先端部を微小隙間を残して閉塞する内側シールケース１３とを有する。外側シールケース１２には、その内径面に、半径方向内方に延在した芯金１４と、この芯金１４の内側内輪寄りで同じく半径方向内方に延在した仕切板１６が固着される。仕切板１６の延在端は内側シールケース１３の外径面にラビリンス隙間を残して近接する。芯金１４の先端には弾性シール部材１７が固着される。この弾性シール部材１７は断面二股状をなし、内側シールケース１３の外径面にそれぞれ軽接触する第１リップ部１７ａと第２リップ部１７ｂを有する。これらがグリースが外部に漏れ出るのを防止する主リップを構成する。第１リップ部１７ａと第２リップ部１７ｂを軽接触させるのは、摩擦による発熱の抑制およびリップ部１７ａ，１７ｂの損傷を防止するためである。弾性シール部材１７には第１リップ部１７ａおよび第２リップ部１７ｂから離間して、第３リップ部１７ｃが形成される。この第３リップ部１７ｃは内側シールケース１３の屈曲部１３ａ内面にラビリンス隙間を残して近接する。第３リップ部１７ｃは外部からの異物の侵入を防止するダストリップを構成する。
特開平１１−３３６７７４号公報 特開２００３−４９８５６号公報 Grease is filled between the inner ring 4 and the outer ring 5 in order to lubricate the raceway surfaces of the inner and outer rings. Oil seals 9 and 11 are disposed at the end portions between the inner and outer rings so that grease does not leak out and dust from the outside does not enter between the inner and outer rings. As shown in FIG. 5, the oil seals 9 and 11 are outer seals in which the base end portion is fitted to the inner diameter of the outer ring 5 and the distal end portion extends toward the ring member (rear cover 3). It has a case 12 and an inner seal case 13 that fits on the outer diameter surface of the ring member (rear lid 3) and closes the tip of the outer seal case 12 leaving a minute gap. To the outer seal case 12, a cored bar 14 extending radially inward and a partition plate 16 extending inward in the radial direction near the inner inner ring of the cored bar 14 are fixed to the inner diameter surface thereof. . The extending end of the partition plate 16 is close to the outer diameter surface of the inner seal case 13 leaving a labyrinth gap. An elastic seal member 17 is fixed to the tip of the core metal 14. The elastic seal member 17 has a bifurcated cross section, and has a first lip portion 17a and a second lip portion 17b that are in light contact with the outer diameter surface of the inner seal case 13, respectively. These constitute the main lip that prevents the grease from leaking out. The reason why the first lip portion 17a and the second lip portion 17b are brought into light contact is to suppress heat generation due to friction and prevent damage to the lip portions 17a and 17b. The elastic seal member 17 is formed with a third lip portion 17c spaced from the first lip portion 17a and the second lip portion 17b. The third lip portion 17c is close to the inner surface of the bent portion 13a of the inner seal case 13 leaving a labyrinth gap. The third lip portion 17c constitutes a dust lip that prevents entry of foreign matter from the outside.
JP-A-11-336774 JP 2003-49856 A

従来のオイルシールは車軸が通常回転数の範囲内であれば安定したシール性能を発揮する。しかし、例えば２３３０ｒｐｍ（３６０ｋｍ／ｈ）以上の高速回転では、軸受内のグリースが漏れ出す場合があり、密封信頼性の点では改善する余地があった。  Conventional oil seals exhibit stable sealing performance as long as the axle is within the normal rotational speed range. However, at high speed rotation of 2330 rpm (360 km / h) or more, for example, grease in the bearing may leak out, and there is room for improvement in terms of sealing reliability.

本発明は、従来のオイルシールの構造を大幅に変えることなく、したがって部品点数も殆ど増大させることなく効果的なラビリンス隙間を追加することでオイルシールの密封性を向上させ、低発熱、耐水性、耐ダスト性を備えた鉄道車両用軸受を提供する。  The present invention improves the seal performance of the oil seal by adding an effective labyrinth gap without significantly changing the structure of the conventional oil seal, and thus increasing the number of parts, and has low heat generation and water resistance. The present invention provides a railway vehicle bearing having dust resistance.

本発明は、車軸に装着される内輪と、前記内輪の外周に複数の転動体を挟んで配設される外輪と、前記車軸に装着されて車軸に対する前記内輪の軸方向位置を規制するリング部材と、前記内輪とリング部材の両幅面間に介設した環状スペーサとを有する鉄道車両用軸受において、前記環状スペーサを異材プレートで構成すると共に、前記環状スペーサの外径側周縁部を、前記幅面を超えて半径方向外方に延在させ、かつ、前記外輪の内径に基端部が嵌合し先端部が前記リング部材側に延在する外側シールケースの内径面にラビリンス隙間を残して近接させたことを特徴とする。   The present invention includes an inner ring that is mounted on an axle, an outer ring that is disposed with a plurality of rolling elements on an outer periphery of the inner ring, and a ring member that is mounted on the axle and restricts the axial position of the inner ring with respect to the axle. And an annular spacer interposed between both width surfaces of the inner ring and the ring member, wherein the annular spacer is formed of a different material plate, and the outer peripheral side peripheral portion of the annular spacer is the width surface. , Extending radially outward and close to the inner diameter surface of the outer seal case where the base end is fitted to the inner diameter of the outer ring and the distal end extends to the ring member side, leaving a labyrinth gap. It is characterized by that.

従来の鉄道車両用車軸のオイルシールでも図５のように環状スペーサ２０は存在するが、従来は環状スペーサ２０の先端が内輪とリング部材の互いに当接する幅面の範囲内にある。また、仕切板１６が弾性シール部材の内側に設けられるが、この仕切板１６の内径端は内側シールケース１３の外径面にラビリンス隙間を残して近接する。このラビリンス隙間は転動体から直接見える位置であり、車軸方向に弾性シール部材１７へと直線的に連通する。このため、車軸の高速回転時に転動体から飛散したグリースの一部がラビリンス隙間を抜けて直接弾性シール部材１７に衝突し、そのリップ部１７ａ，１７ｂを跳ね上げて外部に漏出する可能性がある。本発明は環状スペーサ２０の外径端を外側シールケース１２に近接するまで延在させるため、転動体６から弾性シール材１７が直接見通せない位置関係となる。したがって、車軸高速回転時でのオイルシールの漏出抑制効果が高まる。  Even in the conventional oil seal of a railcar axle, the annular spacer 20 exists as shown in FIG. 5, but conventionally, the tip of the annular spacer 20 is within the range of the width surface where the inner ring and the ring member abut against each other. Further, the partition plate 16 is provided inside the elastic seal member, and the inner diameter end of the partition plate 16 is close to the outer diameter surface of the inner seal case 13 with a labyrinth gap. The labyrinth gap is a position that is directly visible from the rolling elements, and communicates linearly with the elastic seal member 17 in the axle direction. For this reason, there is a possibility that a part of the grease scattered from the rolling element at the time of high speed rotation of the axle collides with the elastic seal member 17 directly through the labyrinth gap, and jumps up the lip portions 17a and 17b to leak outside. . In the present invention, the outer diameter end of the annular spacer 20 is extended to the vicinity of the outer seal case 12, so that the elastic sealing material 17 cannot be directly seen from the rolling element 6. Therefore, the oil seal leakage suppression effect during high-speed rotation of the axle is enhanced.

内輪とリング部材の幅面内にある環状スペーサの両側には、従来と同様に摩耗粉の漏出を防止する弾性シール部材を挟設することができる。これにより環状スペーサと弾性シール部材を別々に組み込む煩雑さがなくなり、組み立て性が向上する。  Elastic seal members that prevent wear powder from leaking out can be sandwiched between both sides of the annular spacer in the width surface of the inner ring and the ring member. This eliminates the trouble of separately incorporating the annular spacer and the elastic seal member, and improves the assemblability.

環状スペーサの外径端は直線状に外側シールケースに近接させるほか、外径端を軸受側に直角に折曲するか、あるいは軸受側に傾斜して折曲し、これによりラビリンス隙間の長さを稼いでグリースの漏出防止効果をさらに確実なものにできる。環状スペーサの外径端に必要に応じてシール材を取り付け、このシール材の外側シールケース側の面を凹凸面にするなどしてラビリンス効果を高めることができる。  The outer diameter end of the annular spacer is placed close to the outer seal case in a straight line, and the outer diameter end is bent at a right angle to the bearing side or inclined at the bearing side, thereby the length of the labyrinth gap. Earn a more reliable grease leakage prevention effect. The labyrinth effect can be enhanced by attaching a sealing material to the outer diameter end of the annular spacer as necessary and making the surface of the sealing material on the outer seal case side uneven.

本発明の鉄道車両用車軸は、従来型車軸の内輪とリング部材の両幅面間に挟み込んだスペーサの形を僅かに変更することで効果的なラビリンス隙間を追加することができ、車軸高速回転時の車軸内グリースの漏出を効果的に阻止することができる。また、環状スペーサが車軸と共に回転することにより軸受内からラビリンス隙間を通り外部へ漏れ出ようとするグリースをスリンガー効果で軸受内へと再循環させることができる。   The railcar axle according to the present invention can add an effective labyrinth gap by slightly changing the shape of the spacer sandwiched between the inner race of the conventional axle and the width surface of the ring member. The leakage of grease in the axle can be effectively prevented. Further, when the annular spacer rotates together with the axle, grease that leaks from the inside of the bearing through the labyrinth gap to the outside can be recirculated into the bearing by the slinger effect.

以下に本発明の一実施形態を図１〜図４に基づいて説明する。図４は従来の鉄道車両用車軸を示すが、スペーサ以外は本発明と同じであるから必要部分を援用する。本発明は図４の鉄道車両の車軸に用いられるものであり、軸受１とその内輪４の両側に各々接して設けられたリング部材としての油切り２および後ろ蓋３を有する。軸受１は、ころ軸受、詳しくは複列の円すいころ軸受からなり、各列のころ６，６に対して設けた分割型の内輪４，４と、一体型の外輪５と、前記ころ６，６と、保持器７と、前記両内輪４，４間に設けられた内輪間座８とで構成される。軸受１の内外輪４，５は軸受鋼または浸炭鋼製であり、油切り２および後ろ蓋３は焼きならしを施した炭素鋼製である。軸受１は、円筒ころ軸受であっても良い。   Hereinafter, an embodiment of the present invention will be described with reference to FIGS. Although FIG. 4 shows a conventional railcar axle, since it is the same as that of the present invention except for the spacer, a necessary part is used. The present invention is used for the axle of the railway vehicle shown in FIG. 4 and has a bearing 1 and an oil drain 2 and a rear lid 3 as ring members provided on both sides of the inner ring 4 respectively. The bearing 1 is composed of a roller bearing, specifically, a double row tapered roller bearing. The split inner rings 4 and 4 provided for the rollers 6 and 6 in each row, the integral outer ring 5, and the rollers 6 and 6. 6, a cage 7, and an inner ring spacer 8 provided between the inner rings 4 and 4. The inner and outer rings 4 and 5 of the bearing 1 are made of bearing steel or carburized steel, and the oil drain 2 and the rear lid 3 are made of normalized carbon steel. The bearing 1 may be a cylindrical roller bearing.

油切り２は、車軸に取付けられて外周にオイルシール９を摺接させる。オイルシール９は外輪５に幅方向に突出して取付けられたリング状のシールケース１０の内周に取付けられる。後ろ蓋３は、車軸に軸受１よりも中央側で取付けられて外周にオイルシール１１を摺接させる。オイルシール１１は外輪５に幅方向に突出して取付けられたリング状のシールケース１２の内周に取付けられる。このシールケース１２および前記油切り２側のシールケース１０は、外輪５を取付けるハウジング（図示せず）に取付けられたものであっても良い。   The oil drain 2 is attached to the axle so that the oil seal 9 is brought into sliding contact with the outer periphery. The oil seal 9 is attached to the inner periphery of a ring-shaped seal case 10 attached to the outer ring 5 so as to protrude in the width direction. The rear lid 3 is attached to the axle on the center side with respect to the bearing 1 and slidably contacts the oil seal 11 on the outer periphery. The oil seal 11 is attached to the inner periphery of a ring-shaped seal case 12 that is attached to the outer ring 5 so as to protrude in the width direction. The seal case 12 and the seal case 10 on the oil drain 2 side may be attached to a housing (not shown) to which the outer ring 5 is attached.

内輪４（大鍔端面）とリング部材（後ろ蓋）３の互いに当接する両幅面には環状スペーサ２０が挟み込まれている。この環状スペーサは内輪４、油切り２、および後ろ蓋３のいずれとも異なる材質、好ましくはこれらの部品２〜４よりも軟質の例えば黄銅製プレートであり、薄板リング状のものである。環状スペーサ２０の径方向幅、つまり内径および外径間の幅は、この環状スペーサ２０を介在させない場合に内輪４と油切り２，後ろ蓋３とが接触する範囲の全体にわたる幅とされている。内輪４とリング部材３の互いに当接する両幅面の外周部はＬ字状に切り欠かれ、左右一対の環状の溝部３１，３２が形成される。この溝部３１，３２内に幅面で発生する摩耗粉の漏出防止用としてＯリング３３が嵌合され、環状スペーサ２０との間の隙間をシールする。Ｏリング３３を設ける代わりに、環状スペーサ２０の両側面にゴム材を環状に接着しても同様の摩耗粉漏出防止作用が得られる。  An annular spacer 20 is sandwiched between both width surfaces of the inner ring 4 (large end surface) and the ring member (rear lid) 3 that are in contact with each other. The annular spacer is a material different from any of the inner ring 4, the oil drain 2 and the rear lid 3, preferably a plate made of brass, for example, which is softer than these components 2 to 4, and is a thin ring shape. The width in the radial direction of the annular spacer 20, that is, the width between the inner diameter and the outer diameter, is the width over the entire range in which the inner ring 4 contacts the oil drainer 2 and the rear lid 3 when the annular spacer 20 is not interposed. . The outer peripheral portions of both width surfaces of the inner ring 4 and the ring member 3 that are in contact with each other are cut out in an L shape, and a pair of left and right annular grooves 31 and 32 are formed. An O-ring 33 is fitted in the groove portions 31 and 32 to prevent leakage of abrasion powder generated on the width surface, and seals the gap between the annular spacer 20. The same action of preventing wear powder leakage can be obtained by adhering a rubber material in an annular shape to both side surfaces of the annular spacer 20 instead of providing the O-ring 33.

環状スペーサ２０の外径端は幅面を超えて半径方向外方に延在する。外径端は外側シールケース１２の内径面にラビリンス隙間を残して近接する。環状スペーサ２０の外径端の形状は種々の変形が可能であり、ここでは図１の直角折曲げ形状、図２の傾斜形状および図３のシール材付設形状の三種を例示する。   The outer diameter end of the annular spacer 20 extends radially outward beyond the width surface. The outer diameter end is close to the inner diameter surface of the outer seal case 12 leaving a labyrinth gap. Various modifications are possible for the shape of the outer diameter end of the annular spacer 20, and here, three types of shapes, that is, a right-angle bent shape of FIG. 1, an inclined shape of FIG.

図１は外径端を軸受方向に直角に折曲させたもので、折曲部２０ａの外側面が外側シールケース１２の内径面に折曲部の全幅にわたるラビリンス隙間を残して近接する。環状スペーサ２０の外径端を単に直線的に半径方向外方に延在させるだけでは外径端と外側シールケース１２の内径面との間のラビリンス効果が限定的である。折曲部２０ａを形成することによりラビリンス隙間の長さを稼ぐことができ、ラビリンス効果が高まる。  In FIG. 1, the outer diameter end is bent at right angles to the bearing direction, and the outer surface of the bent portion 20 a comes close to the inner diameter surface of the outer seal case 12 leaving a labyrinth gap across the entire width of the bent portion. The labyrinth effect between the outer diameter end and the inner diameter surface of the outer seal case 12 is limited simply by extending the outer diameter end of the annular spacer 20 linearly outward in the radial direction. By forming the bent portion 20a, the length of the labyrinth gap can be earned, and the labyrinth effect is enhanced.

図２は環状スペーサ２０の外径端を軸受側に傾斜させつつ半径方向外方に所定長さだけ延在させたものである。この場合も傾斜部２０ｂの外側面が外側シールケース１２の内径面（直角に張り出した肩部１２ａ）と所定長さにわたりラビリンス隙間を形成するから、図１と同様にラビリンス効果が高まる。図２の場合は外径端が傾斜していることにより、軸受内から環状スペーサ２０の内側面に接触して遠心力で半径方向外方に飛ばされたグリースが、傾斜部２０ｂの内側面に案内され、図１の構造よりもさらにスムーズに軸受側に戻される効果がある。  In FIG. 2, the outer diameter end of the annular spacer 20 is extended outward in the radial direction by a predetermined length while being inclined toward the bearing side. Also in this case, since the outer side surface of the inclined portion 20b forms a labyrinth gap over a predetermined length with the inner diameter surface of the outer seal case 12 (the shoulder portion 12a projecting at right angles), the labyrinth effect is enhanced as in FIG. In the case of FIG. 2, since the outer diameter end is inclined, the grease that has contacted the inner surface of the annular spacer 20 from the inside of the bearing and has been blown radially outward by centrifugal force is applied to the inner surface of the inclined portion 20 b. There is an effect that it is guided and returned to the bearing side more smoothly than the structure of FIG.

図３は環状スペーサ２０自体の形状は図１と同じであるが、環状スペーサ２０の外径端にシール材３４を付設した点が異なる。このシール材３４は折曲部２０ａ全体を一定厚さで被覆する形で取り付ける。シール材３４は適度の弾性のあるゴム製または樹脂製が望ましい。シール材３４の外側シールケース１２内径面に向いた面を凹凸面３４ａとすることにより、凹凸面３４ａに対するグリースの付着性が高まり、ラビリンス隙間によるグリース漏出防止効果を増大させる。シール材３４と外側シールケース１２とは非接触を原則とするが、シール材３４の材質によっては軽接触とすることも可能である。  3 is the same as FIG. 1 in the shape of the annular spacer 20 itself, but differs in that a sealing material 34 is attached to the outer diameter end of the annular spacer 20. The sealing material 34 is attached so as to cover the entire bent portion 20a with a constant thickness. The sealing material 34 is desirably made of rubber or resin having moderate elasticity. By setting the surface of the sealing material 34 facing the inner diameter surface of the outer seal case 12 to be a concavo-convex surface 34a, the adhesion of grease to the concavo-convex surface 34a is enhanced, and the grease leakage preventing effect by the labyrinth gap is increased. In principle, the sealing material 34 and the outer sealing case 12 are not in contact with each other. However, depending on the material of the sealing material 34, it is possible to make light contact.

環状スペーサ２０の内径端は、内輪４幅面に形成した段部外径面４ａに圧嵌合される。これにより環状スペーサ２０を内輪４に一体化した状態での組み付けが可能となり、組み付け作業性が向上する。  The inner diameter end of the annular spacer 20 is press-fitted to a stepped portion outer diameter surface 4 a formed on the inner ring 4 width surface. As a result, it is possible to assemble the annular spacer 20 in the state of being integrated with the inner ring 4, and the assembling workability is improved.

以上、本発明の実施形態につき説明したが、本発明は前記実施形態に限定されることなく、種々の変形が可能である。例えば前記実施形態では環状スペーサを黄銅板製としたが、繰り返し荷重に十分耐え得る他の材料で環状スペーサを形成してもよい。   As mentioned above, although it demonstrated per embodiment of this invention, this invention is not limited to the said embodiment, A various deformation | transformation is possible. For example, in the above embodiment, the annular spacer is made of a brass plate, but the annular spacer may be formed of another material that can sufficiently withstand repeated loads.

本発明の第１実施形態に係る鉄道車両用車軸のオイルシール付近の断面図。Sectional drawing of the oil seal vicinity of the axle for railway vehicles which concerns on 1st Embodiment of this invention. 本発明の第２実施形態に係る鉄道車両用車軸のオイルシール付近の断面図。Sectional drawing of the oil seal vicinity of the axle for railway vehicles which concerns on 2nd Embodiment of this invention. 本発明の第３実施形態に係る鉄道車両用車軸のオイルシール付近の断面図。Sectional drawing of the oil seal vicinity of the axle for railway vehicles which concerns on 3rd Embodiment of this invention. 従来の鉄道車両用車軸の断面図。Sectional drawing of the axle for conventional railway vehicles. 従来の鉄道車両用車軸のオイルシール付近の断面図。Sectional drawing of the oil seal vicinity of the axle for conventional railway vehicles.

符号の説明Explanation of symbols

1 軸受
2, 3 リング部材
4 内輪
4a 段部外径面
6 ころ
5 外輪
7 保持器
8 内輪間座
9, 11 オイルシール
12 外側シールケース
13 内側シールケース
13a 屈曲部
14 芯金
16 仕切板
17 弾性シール部材
17a リップ部
17b リップ部
17c リップ部
20 環状プレート
20a 折曲部
20b 傾斜部
31,32 溝部
33 Ｏリング
34 シール材 1 Bearing
2, 3 Ring member
4 Inner ring
4a Step outside diameter surface
6
5 Outer ring
7 Cage
8 Inner ring spacer
9, 11 Oil seal
12 Outer seal case
13 Inner seal case
13a Bend
14 Core
16 Partition plate
17 Elastic seal member
17a Lip part
17b Lip part
17c Lip part
20 Annular plate
20a Folding part
20b ramp
31,32 Groove
33 O-ring
34 Sealing material

Claims (5)

車軸に装着される内輪と、前記内輪の外周に複数の転動体を挟んで配設される外輪と、前記車軸に装着されて車軸に対する前記内輪の軸方向位置を規制するリング部材と、前記内輪とリング部材の両幅面間に介設した環状スペーサとを有する鉄道車両用軸受において、
前記環状スペーサを異材プレートで構成すると共に、前記環状スペーサの外径側周縁部を、前記幅面を超えて半径方向外方に延在させ、かつ、前記外輪の内径に基端部が嵌合し先端部が前記リング部材側に延在する外側シールケースの内径面にラビリンス隙間を残して近接させたことを特徴とする鉄道車両用軸受。 An inner ring mounted on an axle; an outer ring disposed with a plurality of rolling elements on an outer periphery of the inner ring; a ring member mounted on the axle and restricting the axial position of the inner ring with respect to the axle; and the inner ring And a railway vehicle bearing having an annular spacer interposed between both width surfaces of the ring member,
The annular spacer is made of a dissimilar material plate, the outer circumferential side peripheral portion of the annular spacer extends radially outward beyond the width surface, and the base end is fitted to the inner diameter of the outer ring. A railcar bearing characterized in that a tip end portion is close to an inner diameter surface of an outer seal case extending toward the ring member side, leaving a labyrinth gap. 前記両幅面の外周部と環状スペーサとの間に、弾性シール部材を挟設したことを特徴とする請求項１記載の鉄道車両用軸受。 The railway vehicle bearing according to claim 1, wherein an elastic seal member is interposed between the outer peripheral portions of the both width surfaces and the annular spacer. 前記環状スペーサの外径端を軸受側に直角に折曲し、この折曲部の外側面を前記外側シールケースの内径面にラビリンス隙間を残して平行に近接させたことを特徴とする請求項１または２記載の鉄道車両用軸受。 The outer diameter end of the annular spacer is bent at a right angle to the bearing side, and the outer side surface of the bent portion is made close to the inner diameter surface of the outer seal case in parallel, leaving a labyrinth gap. The bearing for railway vehicles according to 1 or 2. 前記環状スペーサの外径端を軸受側に傾斜して折曲し、この折曲部の先端を前記外側シールケースの内径面にラビリンス隙間を残して近接させたことを特徴とする請求項１または２記載の鉄道車両用軸受。 The outer diameter end of the annular spacer is bent to be inclined toward the bearing, and the tip of the bent portion is brought close to the inner diameter surface of the outer seal case leaving a labyrinth gap. 2. Railway vehicle bearing according to 2. 前記環状スペーサの外径端にシール材を設けたことを特徴とする請求項１から４のいずれか記載の鉄道車両用軸受。 The railcar bearing according to any one of claims 1 to 4, wherein a sealing material is provided at an outer diameter end of the annular spacer.
JP2004142550A 2004-05-12 2004-05-12 Bearing for railroad car Withdrawn JP2005325867A (en)

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009113765A (en) * 2007-11-09 2009-05-28 Sumitomo Metal Ind Ltd Gear unit for railway vehicle
JP2011058522A (en) * 2009-09-08 2011-03-24 Nsk Ltd Hub unit for supporting wheel with encoder
CN103062072A (en) * 2011-10-18 2013-04-24 日立汽车系统株式会社 Water pump of internal combustion engine
FR2984432A1 (en) * 2011-12-16 2013-06-21 Ntn Snr Roulements Bearing unit for use on driving shaft of railway vehicle wheel, has movable functional interaction body engaging with fixed functional interaction body to form functional clearance to restrict passage of lubricating and outer material
JP2014005904A (en) * 2012-06-26 2014-01-16 Jtekt Corp Bearing device for axle
JP2018048658A (en) * 2016-09-20 2018-03-29 Ntn株式会社 Bearing device for axle
CN108131398A (en) * 2017-12-25 2018-06-08 中浙高铁轴承有限公司 A kind of labyrinth non-contact sealing for high-speed EMUs axle box bearing

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009113765A (en) * 2007-11-09 2009-05-28 Sumitomo Metal Ind Ltd Gear unit for railway vehicle
JP2011058522A (en) * 2009-09-08 2011-03-24 Nsk Ltd Hub unit for supporting wheel with encoder
US9441675B2 (en) 2011-10-18 2016-09-13 Hitachi Automotive Systems, Ltd. Water pump of internal combustion engine with a slinger sealing the bearing
JP2013087855A (en) * 2011-10-18 2013-05-13 Hitachi Automotive Systems Ltd Water pump of internal combustion engine
CN103062072A (en) * 2011-10-18 2013-04-24 日立汽车系统株式会社 Water pump of internal combustion engine
FR2984432A1 (en) * 2011-12-16 2013-06-21 Ntn Snr Roulements Bearing unit for use on driving shaft of railway vehicle wheel, has movable functional interaction body engaging with fixed functional interaction body to form functional clearance to restrict passage of lubricating and outer material
JP2014005904A (en) * 2012-06-26 2014-01-16 Jtekt Corp Bearing device for 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
CN109661523A (en) * 2016-09-20 2019-04-19 Ntn株式会社 Axle bearing arrangement
GB2569494A (en) * 2016-09-20 2019-06-19 Ntn Toyo Bearing Co Ltd Bearing device for axle
US20190195283A1 (en) * 2016-09-20 2019-06-27 Ntn Corporation Bearing device for axle
US10851839B2 (en) * 2016-09-20 2020-12-01 Ntn Corporation Bearing device for axle
GB2569494B (en) * 2016-09-20 2022-02-09 Ntn Toyo Bearing Co Ltd Bearing device for axle
CN108131398A (en) * 2017-12-25 2018-06-08 中浙高铁轴承有限公司 A kind of labyrinth non-contact sealing for high-speed EMUs axle box bearing

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