JP2006083945A - Railroad vehicle - Google Patents

Railroad vehicle Download PDF

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Publication number
JP2006083945A
JP2006083945A JP2004269403A JP2004269403A JP2006083945A JP 2006083945 A JP2006083945 A JP 2006083945A JP 2004269403 A JP2004269403 A JP 2004269403A JP 2004269403 A JP2004269403 A JP 2004269403A JP 2006083945 A JP2006083945 A JP 2006083945A
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Japan
Prior art keywords
oil
axle
rear lid
bearing
wheel seat
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JP2004269403A
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Japanese (ja)
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JP4047846B2 (en
Inventor
Kenjiro Kamibayashi
賢治郎 上林
Katsutaka Hayashi
克高 林
Toru Konokawa
徹 此川
Yasuyuki Fukui
康之 福井
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Nippon Sharyo Ltd
Central Japan Railway Co
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Nippon Sharyo Ltd
Central Japan Railway Co
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Priority to JP2004269403A priority Critical patent/JP4047846B2/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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6666—Details of supply of the liquid to the bearing, e.g. passages or nozzles from an oil bath in the bearing housing, e.g. by an oil ring or centrifugal disc
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To expand the volume of an annular flow passage part in a rear cover side inside an axle box supporting an axle via a double row tapered roller bearing. <P>SOLUTION: In an axle support mechanism for railroad vehicle, an axle end part of the axle 1 in which a wheel 2 is fitted into a wheel seat 1c is supported by the axle box 4 via the double row tapered roller bearing 3. An end part 4b in a dust guard seat side of the axle box 4 is extended toward the wheel seat direction, and a bearing press part 7a and wheel seat side end part 7h of a rear cover 7 are extended toward the axial direction of the axle 1, such that a labyrinth seal 8 adjoins the wheel seat 1. A fitting position 7g of an oil seal 9 of the rear cover 7 and a sliding position 6d of a lip part 9a of the oil seal 9 of an oil thrower 6 are positioned on the wheel seat side outer periphery of a dust guard seat 1d. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、鉄道車両の車軸支持機構に関し、詳しくは、輪座に車輪を嵌合した車軸の軸端部を軸箱に回転可能に支承する複列円錐ころ軸受の転動体を潤滑油で油浴させる車軸支持機構に関する。   The present invention relates to an axle support mechanism for a railway vehicle, and more specifically, lubricates a rolling element of a double row tapered roller bearing that rotatably supports an axle end portion of an axle having a wheel fitted to a wheel seat on an axle box. The present invention relates to an axle support mechanism for bathing.

近年、新幹線等の高速鉄道車両の車軸支持機構では、車軸を支承する軸受に、走行安定性の観点から左右方向の隙間を小さくできる複列円錐ころ軸受が採用されており、該複列円錐ころ軸受の転動体を潤滑する方式として潤滑油で油浴させるものがある（例えば、特許文献１参照。）。   In recent years, in the axle support mechanism of a high-speed railway vehicle such as a Shinkansen, a double-row tapered roller bearing that can reduce a gap in the left-right direction from the viewpoint of running stability has been adopted as a bearing that supports the axle. As a method of lubricating the rolling elements of the bearing, there is a method in which an oil bath is used with a lubricating oil (see, for example, Patent Document 1).

すなわち、図１０に例示されるように、車軸１は、通常両端部に軸端側からジャーナル１ｅ、ちりよけ座１ｄ、輪座１ｃが順に形成されていて、ジャーナル１ｅに嵌合した複列円錐ころ軸受３を介して軸箱４に支承されている。この支承部の機構は、前記車軸１のジャーナル１ｅに外嵌した前記軸受３の内輪３ａの軸端側と反軸端側とを、軸端側に固定した軸受押さえ５と前記ジャーナル１ｅの反軸端側のちりよけ座１ｄに固定した油切り６とで位置決めし、前記軸箱４に内嵌した前記軸受３の外輪３ｂの軸端側と反軸端側とを、前記軸箱４の軸端側に形成された鍔部４ａと前記軸箱４のちりよけ座側端部４ｂに固定した後蓋７の軸受押さえ部７ａとで位置決めし、該後蓋７の輪座側端部７ｈと前記油切り６との間にラビリンスシール８を形成し、前記後蓋７の軸受押さえ部７ａの内周面の前記ラビリンスシール寄りに嵌合させたオイルシール９のリップ部９ａを前記油切り６の外周面に摺接し、前記軸箱４の下部内面に軸受潤滑油の油溜め１０を凹設し、前記軸箱４の軸端部４ｃを前蓋１１で塞いでいる。   That is, as illustrated in FIG. 10, the axle 1 has a double row in which a journal 1e, a dust seat 1d, and a wheel seat 1c are normally formed at both ends from the shaft end side in order. It is supported on a shaft box 4 via a tapered roller bearing 3. The mechanism of this support portion is a structure in which the shaft end side and the non-shaft end side of the inner ring 3a of the bearing 3 externally fitted to the journal 1e of the axle 1 are fixed to the shaft end side and the bearing press 5 and the journal 1e are opposite to each other. The shaft end side and the opposite end side of the outer ring 3b of the bearing 3 which are positioned with the oil drain 6 fixed to the dust-proof seat 1d on the shaft end side and fitted in the shaft box 4 are connected to the shaft box 4 Positioning by the flange 4a formed on the shaft end side and the bearing pressing portion 7a of the rear lid 7 fixed to the dust guard side end portion 4b of the axle box 4, and the wheel seat side end of the rear lid 7 A labyrinth seal 8 is formed between the portion 7 h and the oil drain 6, and a lip portion 9 a of the oil seal 9 fitted to the inner peripheral surface of the bearing pressing portion 7 a of the rear lid 7 close to the labyrinth seal is An oil sump 10 for bearing lubricating oil is recessedly provided on the lower inner surface of the axle box 4 in sliding contact with the outer peripheral surface of the oil drain 6, and the axle box 4 The axial end portion 4c is blocking in front of the lid 11.

そして、前記複列円錐ころ軸受３の回転時に転動体３ｃを油浴させるために、前記油溜め１０から前記転動体３ｃを油浴して油溜め１０に循環する潤滑油の流路を、前記軸受３と前記前蓋１１との間に画成される前蓋側環状流路部１２と、前記軸受３と前記オイルシール９との間に画成される後蓋側環状流路部１３と、前記鍔部４ａの下部に形成した前記油溜め１０と前記前蓋側環状流路部１２とを連通する凹溝状の前蓋側流路部４ｄと、前記軸箱４の後蓋側の下部に形成した前記油溜め１０と前記後蓋側環状流路部１３とを連通する凹溝状の後蓋側流路部４ｅと、前記軸受押さえ部７ａの下部を切り欠いて前記後蓋側流路部４ｅと前記後蓋側環状流路部１３とを連通する切り欠き流路部７ｄとで構成している。   Then, in order to oil bath the rolling elements 3c when the double row tapered roller bearing 3 rotates, a lubricating oil flow path that circulates the rolling elements 3c from the oil reservoir 10 to the oil reservoir 10 through the oil reservoir, A front lid side annular flow path portion 12 defined between the bearing 3 and the front lid 11; and a rear lid side annular flow path portion 13 defined between the bearing 3 and the oil seal 9; A groove-shaped front lid side flow passage portion 4d communicating the oil sump 10 formed at the lower portion of the flange portion 4a and the front lid side annular flow passage portion 12, and a rear lid side of the axle box 4 A groove-shaped rear lid side flow passage portion 4e communicating the oil sump 10 formed at the lower portion with the rear lid side annular flow passage portion 13 and a lower portion of the bearing holding portion 7a are cut out to form the rear lid side. The channel portion 4e and the rear lid side annular channel portion 13 are configured by a notched channel portion 7d that communicates with the channel portion 4e.

前記油溜め１０には、前記転動体３ｃのピッチ円直径付近に油面Ｆが位置するように潤滑油が溜められており、前記軸受３の回転に伴って、前記外輪３ｂの下部中央部分に形成された供給孔３ｆから潤滑油が内輪３ａ及び転動体３ｃによって上方へ運ばれ、転動体３ｃの小径側から大径側、すなわち、軸受３の中央部分から外側へ潤滑油が流れて転動体３ｃを潤滑し、前記前蓋側環状流路部１２と前記後蓋側環状流路部１３とから前記油溜め１０に循環する。
特開２００４−１６２８８３号公報 第１〜３頁 図１〜３ Lubricating oil is stored in the oil sump 10 so that the oil surface F is located near the pitch circle diameter of the rolling element 3c. As the bearing 3 rotates, the oil sump 10 is provided at the lower central portion of the outer ring 3b. Lubricating oil is conveyed upward from the formed supply hole 3f by the inner ring 3a and the rolling element 3c, and the lubricating oil flows from the small diameter side of the rolling element 3c to the large diameter side, that is, from the central portion of the bearing 3 to the outside, thereby rolling the rolling element. 3c is lubricated and circulated from the front lid side annular flow path portion 12 and the rear lid side annular flow path portion 13 to the oil sump 10.
JP, 2004-162883, A page 1-3 pages 1-3

ところが、上述の構造は、輪座１ｃに圧入嵌合されている車輪をジャーナル１ｅ側へ移動（約５０ｍｍ）させて、車軸１の探傷検査を行うことを対象として設計されたものであるため、後蓋７と輪座１ｃに圧入嵌合されている車輪との間に車輪を移動させる間隙を大きく採らなければならなかった。したがって、軸箱４の車体幅方向の長さが、例えば、軸受３の車体幅方向中央部Ｃ１から軸箱４の車外側端までの長さが１０５ｍｍであるのに対し、前記中央部Ｃ１から軸箱４の車内側端までの長さが９７．５ｍｍしか確保できず、前記ラビリンスシール８が前記車軸１のちりよけ座１ｄの輪座側の外周に位置し、これにより、前記後蓋７のオイルシール９の嵌合位置と前記油切り６のオイルシール９のリップ部９ａの摺接位置とが、前記車軸１のちりよけ座１ｄのジャーナル側外周に位置せざるを得なかった。したがって、前記前蓋側環状流路部１２に比べて前記後蓋側環状流路部１３の容積が小さくなる。上述の構造では、前記前蓋側環状流路部１２の容積を１とすると、前記後蓋側環状流路部１３の容積は０．４程度である。   However, the above-described structure is designed to perform a flaw detection inspection of the axle 1 by moving the wheel press-fitted to the wheel seat 1c to the journal 1e side (about 50 mm). A large gap for moving the wheel had to be taken between the rear lid 7 and the wheel press fitted into the wheel seat 1c. Accordingly, the length in the vehicle body width direction of the axle box 4 is, for example, 105 mm from the vehicle width direction center portion C1 of the bearing 3 to the vehicle outer side end, whereas the length from the center portion C1 is The length of the axle box 4 up to the vehicle inner end can be secured only 97.5 mm, and the labyrinth seal 8 is positioned on the outer periphery of the axle seat 1d on the wheel seat side, whereby the rear cover 7 and the sliding position of the lip portion 9a of the oil seal 9 of the oil drain 6 have to be positioned on the journal side outer periphery of the dust seat 1d of the axle 1. . Therefore, the volume of the rear lid side annular flow path portion 13 is smaller than that of the front lid side annular flow path portion 12. In the above-described structure, when the volume of the front lid side annular flow path portion 12 is 1, the volume of the rear lid side annular flow path portion 13 is about 0.4.

このように、前記後蓋側環状流路部１３の容積が小さいと、軸受の回転数を高くした場合に、前記後蓋側環状流路部１３を流れる潤滑油の流れが滞りやすくなり、潤滑油の温度上昇を招く。潤滑油の温度が高くなることは、実車において安全上の温度管理から非常に重要な事柄である。また、油温の上昇が限界を超えると、スラッジと呼ばれる不溶解物質が潤滑油中に大量に生成され、オイルシール９に噛み込まれ、油漏れの原因となる。このため、走行中の潤滑油温度には使用限界があり、走行速度の向上に大きな障害となっていた。   Thus, if the volume of the rear cover side annular flow path portion 13 is small, the flow of the lubricating oil flowing through the rear cover side annular flow path portion 13 is likely to stagnate when the number of rotations of the bearing is increased. The oil temperature rises. An increase in the temperature of the lubricating oil is a very important matter in terms of safety temperature control in an actual vehicle. When the rise in the oil temperature exceeds the limit, a large amount of insoluble material called sludge is generated in the lubricating oil and is caught in the oil seal 9, causing oil leakage. For this reason, there is a use limit in the lubricating oil temperature during traveling, which has been a major obstacle to improving traveling speed.

しかしながら、その後、車軸に軸方向の貫通孔を形成した中空車軸が開発され、探傷検査技術の向上によって、車輪を輪座から軸箱側へ移動させなくても車軸探傷検査が貫通孔からの非破壊検査で可能となった。   However, after that, a hollow axle having an axial through hole formed in the axle was developed, and by improving the flaw detection inspection technology, the axle flaw inspection can be carried out from the through hole without moving the wheel from the wheel seat to the axle box side. Made possible by destructive inspection.

そこで本発明は、この点に着目し、軸箱のちりよけ座側端部を輪座側へ延長して、軸箱の車体幅方向の長さを確保するとともにオイルシールの配置位置を改善して、後蓋側環状流路部の容積を大きくすることにより、後蓋側環状流路部を流れる潤滑油の温度上昇を抑えて、走行速度の向上に大幅に寄与することができる鉄道車両の車軸支持機構を提供することを目的としている。   Therefore, the present invention pays attention to this point and extends the end portion of the axle box toward the wheel seat side to secure the length of the axle box in the vehicle body width direction and improve the position of the oil seal. Thus, by increasing the volume of the rear lid side annular flow passage portion, the rail vehicle can greatly contribute to the improvement of traveling speed by suppressing the temperature rise of the lubricating oil flowing through the rear lid side annular flow passage portion. The purpose of this invention is to provide an axle support mechanism.

上記した目的を達成するため、本発明は、輪座１ｃに車輪２を嵌合した車軸１の軸端部を複列円錐ころ軸受３を介して軸箱４に支承する鉄道車両の車軸支持機構であって、前記車軸１のジャーナル１ｅに外嵌した前記軸受３の内輪３ａの軸端側と反軸端側とを、軸端側に固定した軸受押さえ５と前記ジャーナル１ｅの反軸端側のちりよけ座１ｂに固定した油切り６とで位置決めし、前記軸箱４に内嵌した前記軸受３の外輪３ｂの軸端側と反軸端側とを、前記軸箱４の軸端側に形成された鍔部４ａと前記軸箱４のちりよけ座側端部４ｂに固定した後蓋７の軸受押さえ部７ａとで位置決めし、該後蓋７の輪座側端部７ｈと前記油切り６との間にラビリンスシール８を形成し、前記後蓋７の軸受押さえ部７ａの内周面の前記ラビリンスシール寄りに嵌合させたオイルシール９のリップ部９ａを前記油切り６の外周面に摺接し、前記軸箱４の下部内面に軸受潤滑油の油溜め１０を凹設し、前記軸箱４の軸端部４ｃを前蓋１１で塞ぎ、前記軸受３の回転時に前記油溜め１０から前記軸受３の転動体３ｃを油浴して油溜め１０に循環する潤滑油の流路を、前記軸受３と前記前蓋１１との間に画成される前蓋側環状流路部１２と、前記軸受３と前記オイルシール９との間に画成される後蓋側環状流路部１３と、前記鍔部４ａの下部に形成した前記油溜め１０と前蓋側環状流路部１２とを連通する凹溝状の前蓋側流路部４ｄと、前記軸箱４の後蓋側の下部に形成した前記油溜め１０と前記後蓋側環状流路部１３とを連通する凹溝状の後蓋側流路部４ｅと、前記軸受押さえ部７ａの下部を切り欠いて前記後蓋側流路部４ｅと前記後蓋側環状流路部１３とを連通する切り欠き流路部７ｄとで構成した車軸支持機構を有する鉄道車両において、前記軸箱４のちりよけ座側端部４ｂを前記輪座方向へ延長するとともに、前記後蓋７の軸受押さえ部７ａと輪座側端部７ｈとを前記車軸１の軸線方向に延長して、前記ラビリンスシール８を前記輪座１ｃに近接させ、前記後蓋７の前記オイルシール９の嵌合位置７ｇと前記油切り６の前記オイルシール９のリップ部９ａの摺接位置６ｄとを前記ちりよけ座１ｄの輪座側外周に位置させ、前記後蓋側環状流路部１３の容積を従来よりも大幅に拡張させたことを特徴としている。また、前記前蓋側環状流路部１２と前記後蓋側環状流路部１３との容積比は、１：０．７から１：１．３程度が好ましい。   In order to achieve the above-described object, the present invention provides an axle support mechanism for a railway vehicle in which a shaft end portion of an axle 1 in which a wheel 2 is fitted to a wheel seat 1c is supported on an axle box 4 via a double row tapered roller bearing 3. A bearing retainer 5 in which the shaft end side and the opposite shaft end side of the inner ring 3a of the bearing 3 fitted on the journal 1e of the axle shaft 1 are fixed to the shaft end side and the opposite shaft end side of the journal 1e. The shaft end of the outer ring 3b of the bearing 3 and the shaft end side of the bearing 3 fitted in the shaft box 4 are positioned with the oil drain 6 fixed to the dust guard 1b. Positioned by a flange portion 4a formed on the side and a bearing holding portion 7a of the rear lid 7 fixed to the end portion 4b of the axle box 4 on the side of the dust guard seat, the wheel seat side end portion 7h of the rear lid 7 A labyrinth seal 8 is formed between the oil drain 6 and the inner circumferential surface of the bearing pressing portion 7a of the rear lid 7 close to the labyrinth seal. The lip portion 9a of the combined oil seal 9 is slidably contacted with the outer peripheral surface of the oil drain 6 and an oil sump 10 for bearing lubricating oil is recessed in the lower inner surface of the axle box 4 so that the shaft end of the axle box 4 4c is closed with a front lid 11, and a lubricating oil passage that circulates from the oil reservoir 10 to the oil reservoir 10 by rolling the rolling element 3c of the bearing 3 from the oil reservoir 10 during rotation of the bearing 3 is provided between the bearing 3 and the front lid 11. A front lid side annular flow passage portion 12 defined between the lid 11, a rear lid side annular flow passage portion 13 defined between the bearing 3 and the oil seal 9, and the flange portion 4 a. A concave groove-like front lid side flow passage portion 4d communicating the oil reservoir 10 and the front lid side annular flow passage portion 12 formed at the lower portion of the shaft box 4, and the oil formed at the lower portion on the rear lid side of the axle box 4. A concave groove-like rear lid side flow passage portion 4e communicating with the reservoir 10 and the rear lid side annular flow passage portion 13 and a lower portion of the bearing holding portion 7a are cut out. In a railway vehicle having an axle support mechanism constituted by a notch channel portion 7d that communicates the rear lid side channel portion 4e and the rear lid side annular channel portion 13, the side of the axle box 4 on the side of the sliding seat The end portion 4b is extended in the wheel seat direction, the bearing pressing portion 7a and the wheel seat side end portion 7h of the rear lid 7 are extended in the axial direction of the axle 1, and the labyrinth seal 8 is attached to the wheel seat. 1c, the fitting position 7g of the oil seal 9 of the rear lid 7 and the sliding contact position 6d of the lip portion 9a of the oil seal 9 of the oil drain 6 are on the wheel seat side of the dust guard 1d. It is located on the outer periphery, and the volume of the rear lid side annular flow path portion 13 is greatly expanded as compared with the prior art. The volume ratio between the front lid side annular flow path portion 12 and the rear lid side annular flow path portion 13 is preferably about 1: 0.7 to 1: 1.3.

以上説明したように、本発明は、後蓋側環状流路部の容積を従来よりも大幅に拡張することにより、後蓋側環状流路部を流れる潤滑油の温度上昇を抑え、スラッジの生成を低減して、オイルシールのシール性を確保できるから、走行速度の向上に大幅に寄与することができる。   As described above, according to the present invention, the volume of the rear lid-side annular flow passage portion is greatly expanded as compared with the conventional case, thereby suppressing the temperature rise of the lubricating oil flowing through the rear lid-side annular flow passage portion, and generating sludge. And the sealing performance of the oil seal can be secured, which can greatly contribute to the improvement of the traveling speed.

以下、本発明を図面に示される実施形態例に基づいて説明する。なお、前記背景技術に記載した各部品と同一要素には同一の符号を付して説明する。軸箱４は、その内部に装着される複列円錐ころ軸受３を介して車軸１を回転可能に支承し、前記車軸１の軸端側を前蓋１１で塞ぎ、反軸端側をリング状の後蓋７で塞いでいる。   Hereinafter, the present invention will be described based on an embodiment shown in the drawings. In addition, the same code | symbol is attached | subjected and demonstrated to the same element as each component described in the said background art. The axle box 4 rotatably supports the axle 1 via a double-row tapered roller bearing 3 mounted therein, the axle end of the axle 1 is closed with a front lid 11, and the opposite axle end is ring-shaped. It is closed with the rear lid 7.

前記車軸１は、軸方向の貫通孔１ａを形成し、該貫通孔１ａを軸端プラグ１ｂで塞いだ中空車軸で、車輪２を輪座１ｃに圧入嵌合し、該輪座１ｃの軸端側に形成されたちりよけ座１ｄに油切り６を圧入固定し、該ちりよけ座１ｄの軸端側に形成されたジャーナル１ｅに前記軸受３の内輪３ａを外嵌して内輪３ａの反軸端側を前記油切り６にて位置決めし、前記ジャーナル１ｅの軸端側に形成されたネジ部１ｆに螺着された軸受押さえ５にて内輪３ａの軸端側を位置決めする。前記軸受押さえ５は、前記ネジ部１ｆの軸端側にスプライン嵌合する回り止めリング２０とボルト２１で結合することにより回り止めされて固定される。   The axle 1 is a hollow axle in which an axial through hole 1a is formed and the through hole 1a is closed with a shaft end plug 1b. The wheel 2 is press-fitted into the wheel seat 1c, and the shaft end of the wheel seat 1c is The oil drain 6 is press-fitted and fixed to the dust guard seat 1d formed on the side, and the inner ring 3a of the bearing 3 is externally fitted to the journal 1e formed on the shaft end side of the dust guard seat 1d so that the inner ring 3a is opposite to the inner ring 3a. The shaft end side is positioned by the oil drain 6 and the shaft end side of the inner ring 3a is positioned by the bearing retainer 5 screwed to the screw portion 1f formed on the shaft end side of the journal 1e. The bearing retainer 5 is locked and fixed by being connected by a bolt 21 with a rotation prevention ring 20 that is spline-fitted to the shaft end side of the screw portion 1f.

前記複列円錐ころ軸受３は、前記内輪３ａと外輪３ｂとの間に転動体３ｃとして小径側を中央に向けた複列円錐ころを配設し、各転動体３ｃを等間隔に保持器３ｄで保持し、前記外輪３ｂの下部中央部分に潤滑油の供給孔３ｆを形成している。   In the double row tapered roller bearing 3, double row tapered rollers having a small diameter side toward the center are disposed as rolling elements 3c between the inner ring 3a and the outer ring 3b, and the rolling elements 3c are arranged at regular intervals. And a lubricating oil supply hole 3f is formed in the lower central portion of the outer ring 3b.

前記軸箱４は、前記外輪３ｂを内嵌し、車両外側となる軸端側に形成された鍔部４ａにて前記外輪３ｂの軸端側を位置決めし、車両内側となる反軸端側となるちりよけ座側端部４ｂに固定される後蓋７の軸受押さえ部７ａにて前記外輪３ｂの反軸端側を位置決めする。この軸箱４は、ちりよけ座側端部４ｂを従来よりも前記輪座方向へ延長して形成されている。例えば、本実施形態例では、前記軸受３の車体幅方向中央部Ｃ１から軸箱４の軸端側の端部４ｃまでの寸法が１０５ｍｍであるのに対し、前記中央部Ｃ１から前記ちりよけ座側端部４ｂまでの寸法が１００ｍｍに形成されている。   The axle box 4 fits the outer ring 3b, positions the shaft end side of the outer ring 3b with a flange 4a formed on the shaft end side that is the vehicle outer side, and the opposite shaft end side that is the vehicle inner side. The opposite shaft end side of the outer ring 3b is positioned by the bearing pressing portion 7a of the rear lid 7 fixed to the dust guard side end portion 4b. The axle box 4 is formed by extending the dust guard side end portion 4b in the direction of the wheel seat as compared with the conventional case. For example, in the present embodiment, the dimension from the center portion C1 of the bearing 3 in the vehicle body width direction to the end portion 4c on the shaft end side of the axle box 4 is 105 mm, whereas from the center portion C1, the dust-proofing is performed. The dimension up to the seat side end 4b is 100 mm.

また、軸箱４には、前記鍔部４ａが軸端側に前記前蓋１１の嵌合代を残して形成され、該鍔部４ａのちりよけ座側の下部内面に、軸受潤滑油の油溜め１０となる凹部が凹設されている。該油溜め１０の軸端側に前記鍔部４ａの下部を凹溝状に切り欠いた前蓋側流路部４ｄが形成されるとともに、反軸端側の下部の中央に凹溝状に切り欠いた第１後蓋側流路部４ｅが形成され、該第１後蓋側流路部４ｅを挟んで第２後蓋側流路部４ｆと第３後蓋側流路部４ｇとが形成されている。前記油溜め１０の底部には、油抜き孔４ｈが設けられ、該油抜き孔４ｈには、磁気栓２２が螺着されている。さらに、軸箱４には、軸端側外周に前記前蓋１１を取り付ける前蓋用フランジ部４ｉが、反軸端側外周に前記後蓋７を取り付ける後蓋用フランジ部４ｊがそれぞれ形成されている。   Further, the shaft box 4 is formed with the flange portion 4a on the shaft end side while leaving the fitting allowance of the front lid 11, and bearing lube oil is provided on the inner surface of the lower portion of the flange portion 4a on the dust guard side. A recess that becomes the oil sump 10 is provided. A front lid-side channel portion 4d is formed on the shaft end side of the oil sump 10 by cutting out the lower portion of the flange portion 4a into a concave groove shape, and is cut into a concave groove shape in the center of the lower portion on the opposite shaft end side. The lacked first rear lid side flow channel portion 4e is formed, and the second rear lid side flow channel portion 4f and the third rear lid side flow channel portion 4g are formed across the first rear lid side flow channel portion 4e. Has been. An oil drain hole 4h is provided at the bottom of the oil sump 10, and a magnetic plug 22 is screwed into the oil drain hole 4h. Further, the axle box 4 is formed with a front lid flange portion 4i for attaching the front lid 11 to the outer periphery of the shaft end side, and a rear lid flange portion 4j for attaching the rear lid 7 to the outer periphery of the opposite shaft end side. Yes.

前記後蓋７は、前記軸箱４のちりよけ座側端部４ｂに内嵌される前記軸受押さえ部７ａと、前記後蓋用フランジ部４ｈにボルト２３にて取り付けられるフランジ部７ｂと、該フランジ部７ｂの反軸端側で前記油切り６との間にラビリンスシール８を形成する蓋部７ｃとで構成されている。前記軸受押さえ部７ａは、前記前記軸箱４のちりよけ座側の端部４ｂが前記輪座方向へ延長して形成されていることから、軸端側の端部を前記車軸１の軸線方向に従来よりも延長して形成されている。この軸受押さえ部７ａの下部には、前記第１後蓋側流路部４ｅに対応する第１切り欠き流路部７ｄが中央部分に切り欠き形成されるとともに、該第１切り欠き流路部７ｄを挟んで、前記第２後蓋側流路部４ｆに対応する第２切り欠き流路部７ｅと、前記第３後蓋側流路部４ｇに対応する第３切り欠き流路部７ｆとが形成されている。前記フランジ部７ｂの内周には、オイルシール９の嵌合部７ｇが形成されている。前記蓋部７ｃは、前記フランジ部７ｂの反軸端側に輪座側端部７ｈを前記車軸１の軸線方向に従来よりも延長して、前記ちりよけ座１ｂと前記輪座１ｃの中間部分の中径部１ｇ外周に形成され、該蓋部７ｃの内周に前記ラビリンスシール８を形成するシール部７ｉが設けられている。   The rear lid 7 includes the bearing pressing portion 7a fitted into the end portion 4b of the axle box 4 and a flange portion 7b attached to the rear lid flange portion 4h with a bolt 23. It is comprised by the cover part 7c which forms the labyrinth seal 8 between the said oil drains 6 in the anti-shaft end side of this flange part 7b. The bearing holding portion 7a is formed by extending the end portion 4b on the side of the axle box 4 in the direction of the wheel seat so that the end portion on the shaft end side is the axis of the axle 1. It is formed to extend in the direction as compared with the conventional one. A first notch channel portion 7d corresponding to the first rear lid side channel portion 4e is formed in the lower portion of the bearing retainer portion 7a, and the first notch channel portion is formed. 7d, a second notch channel portion 7e corresponding to the second rear lid side channel portion 4f, and a third notch channel portion 7f corresponding to the third rear lid side channel portion 4g, Is formed. A fitting portion 7g of the oil seal 9 is formed on the inner periphery of the flange portion 7b. The lid portion 7c is formed by extending a wheel seat side end portion 7h in the axial direction of the axle 1 on the opposite axis end side of the flange portion 7b, so that the intermediate portion between the dust guard seat 1b and the wheel seat 1c. A seal portion 7i that is formed on the outer periphery of the middle diameter portion 1g of the portion and that forms the labyrinth seal 8 is provided on the inner periphery of the lid portion 7c.

前記油切り６は、前記ちりよけ座１ｂの軸端側から前記輪座１ｃの軸端側に亘って外嵌される筒状体で、軸端側の小径部６ａと該小径部６ａの輪座側の中径部６ｂと、該中径部６ｂの輪座側のシール部６ｃとで構成されている。前記小径部６ａは、前記ちりよけ座１ｂの軸端側からちりよけ座１ｂの輪座側の略中間部分の外周に亘って形成され、前記中径部６ｂは、ちりよけ座１ｂの略中間部分から前記中径部１ｇの外周に亘って形成され、前記シール部６ｃは、前記蓋部７ｃのシール部７ｉに対応して、前記ちりよけ座１ｂよりも前記輪座１ｃ側の前記中径部１ｇの外周に形成されている。これにより、前記ラビリンスシール８は、従来よりも前記輪座１ｃに近接して形成されることになる。   The oil drainer 6 is a cylindrical body that is externally fitted from the shaft end side of the dust guard 1b to the shaft end side of the wheel seat 1c, and includes a small diameter portion 6a on the shaft end side and a small diameter portion 6a. It is composed of an intermediate diameter portion 6b on the wheel seat side and a seal portion 6c on the wheel seat side of the intermediate diameter portion 6b. The small-diameter portion 6a is formed from the shaft end side of the dust-proof seat 1b to the outer periphery of a substantially intermediate portion on the wheel seat side of the dust-proof seat 1b, and the medium-diameter portion 6b is formed of the dust-proof seat 1b. The seal portion 6c corresponds to the seal portion 7i of the lid portion 7c so as to be closer to the wheel seat 1c than the dust guard seat 1b. Are formed on the outer periphery of the medium diameter portion 1g. Thereby, the labyrinth seal 8 is formed closer to the wheel seat 1c than in the prior art.

前記オイルシール９は、リップ部９ａと仕切り板９ｂとを有し、前記後蓋７の嵌合部７ｇに嵌合されて前記リップ部９ａを前記油切り６の中径部６ｂに摺接している。このオイルシール９は、前記したように、前記後蓋７の嵌合部７ｇが前記フランジ部７ｂの内周に形成されていることから、その嵌合位置は、前記ちりよけ座１ｂの輪座側外周位置になり、また、前記油切り６の中径部６ｂがちりよけ座１ｂの略中間部分から前記中径部１ｇの外周に亘って形成されていることから、リップ部９ａの摺接位置が前記ちりよけ座１ｂの輪座側外周に位置することなる。   The oil seal 9 has a lip portion 9a and a partition plate 9b. The oil seal 9 is fitted to the fitting portion 7g of the rear lid 7 so that the lip portion 9a is slidably contacted with the middle diameter portion 6b of the oil drain 6. Yes. As described above, since the fitting portion 7g of the rear cover 7 is formed on the inner periphery of the flange portion 7b, the fitting position of the oil seal 9 is the ring of the dust guard 1b. Since it is the seat side outer peripheral position and the middle diameter portion 6b of the oil drain 6 is formed from the substantially middle portion of the dust guard seat 1b to the outer periphery of the middle diameter portion 1g, the lip portion 9a The sliding contact position is located on the outer periphery of the dust guard 1b.

前記前蓋１１は、前記軸箱４の軸端部４ｃに内嵌される嵌合部１１ａと、前記軸箱４の前蓋用フランジ部４ｉにボルトにて取り付けられるフランジ部１１ｂと、前記軸箱４の軸端部４ｃの開口を塞ぐ蓋部１１ｃと、該蓋部１１ｃの車軸端部分に開口する開口部１１ｄと、前記前蓋用フランジ部１１ｂの内周部分に設けられた仕切り鍔部１１ｅとを備えている。前記開口部１１ｄは、ゴムキャップ２４にて閉塞される。また、前記フランジ部１１ｂの上部には、台車枠２５との間にダンパ２６を連結するアーム１１ｆが連設されている。前記仕切り鍔部１１ｅの下部は、前記油溜め１０の予備室１０ａとなるように切り欠かれている。   The front lid 11 includes a fitting portion 11a fitted into the shaft end portion 4c of the axle box 4, a flange portion 11b attached to the front lid flange portion 4i of the axle box 4 by a bolt, and the shaft. A lid portion 11c that closes the opening of the shaft end portion 4c of the box 4, an opening portion 11d that opens to the axle end portion of the lid portion 11c, and a partition flange provided on the inner peripheral portion of the flange portion 11b for the front lid 11e. The opening 11d is closed by a rubber cap 24. In addition, an arm 11f that connects the damper 26 to the carriage frame 25 is connected to the upper portion of the flange portion 11b. The lower part of the partition flange 11e is cut out so as to be a reserve chamber 10a of the oil sump 10.

前記複列円錐ころ軸受３と前記前蓋１１の仕切り鍔部１１ｅとの間には、前蓋側環状流路部１２が画成され、また、前記複列円錐ころ軸受３と前記オイルシール９との間には、後蓋側環状流路部１３が画成されている。前記前蓋側環状流路部１２は、前記前蓋側流路部４ｄを介して前記油溜め１０に連通し、前記後蓋側環状流路部１３は、前記第１切り欠き流路部７ｄ、前記第２切り欠き流路部７ｅ及び前記第３切り欠き流路部７ｆと、前記後蓋側第１流路部４ｅ、後蓋側第２流路部４ｆ及び後蓋側第３流路部４ｇとを介して前記油溜め１０に連通している。   Between the double row tapered roller bearing 3 and the partition collar portion 11e of the front lid 11, a front lid side annular flow passage portion 12 is defined, and the double row tapered roller bearing 3 and the oil seal 9 are formed. The rear lid side annular flow path portion 13 is defined between the two. The front lid side annular flow passage portion 12 communicates with the oil sump 10 via the front lid side flow passage portion 4d, and the rear lid side annular flow passage portion 13 is provided with the first notch flow passage portion 7d. The second notch channel portion 7e and the third notch channel portion 7f, the rear lid side first channel portion 4e, the rear lid side second channel portion 4f, and the rear lid side third channel. The oil sump 10 communicates with the portion 4g.

前記後蓋側環状流路部１３は、前述したように、従来の構造よりも容積が拡張されている。すなわち、前記軸箱４のちりよけ座側の端部４ｂを前記輪座方向へ延長したこと、前記後蓋７の軸受押さえ部７ａと輪座側端部７ｂとを前記車軸１の軸線方向に延長して、前記ラビリンスシール８を前記輪座１ｃに近接させたこと、前記後蓋７の前記オイルシール９の嵌合位置７ｄと前記油切り６の前記オイルシール９のリップ部９ａの摺接位置６ａとを前記ちりよけ座１ｂの輪座側外周に位置させたことにより容積が拡張されている。また、前記油溜め１０の後蓋側に前記第１〜第３後蓋側流路部４ｅ，４ｆ，４ｇを形成したこと、前記後蓋７に前記第１〜第３切り欠き流路部７ｄ，７ｅ，７ｆを形成したことにより、前記後蓋側環状流路部１３と前記油溜め１０間の連通状態も従来の構造よりも改善され、大量の潤滑油が前記後蓋側環状流路部１３から前記油溜め１０に流れる。前記油溜め１０には、前記転動体３ｃのピッチ円直径付近に油面Ｆが位置するように潤滑油が溜められている。   As described above, the rear lid-side annular flow passage portion 13 has a larger volume than the conventional structure. That is, the end 4b of the axle box 4 on the side of the seat is extended in the wheel seat direction, and the bearing pressing portion 7a and the wheel seat side end 7b of the rear lid 7 are connected in the axial direction of the axle 1. The labyrinth seal 8 is extended close to the wheel seat 1c, and the fitting position 7d of the oil seal 9 of the rear lid 7 and the lip portion 9a of the oil seal 9 of the oil drain 6 are slid. The volume is expanded by positioning the contact position 6a on the outer periphery of the dust guard 1b. Further, the first to third rear lid side flow passage portions 4e, 4f, 4g are formed on the rear lid side of the oil sump 10, and the first to third notch flow passage portions 7d are formed on the rear lid 7. , 7e, 7f, the communication state between the rear lid-side annular flow passage portion 13 and the oil sump 10 is also improved as compared with the conventional structure, and a large amount of lubricating oil is added to the rear lid-side annular flow passage portion. 13 to the oil sump 10. Lubricating oil is stored in the oil sump 10 so that the oil level F is positioned near the pitch circle diameter of the rolling elements 3c.

なお、上述の構成であっても、前記後蓋７の輪座側端部７ｈと前記輪座１ｃに嵌合された車輪２との間に、前記軸受３を軸端方向に引き抜くための治具の挿入は可能であり、また、前記輪座１ｃに嵌合された車輪２を軸端方向に３０ｍｍ移動可能であるから、前記輪座１ｃの目視による探傷検査も可能である。   Even in the above-described configuration, the bearing 3 is pulled out in the axial direction between the wheel seat side end portion 7h of the rear lid 7 and the wheel 2 fitted to the wheel seat 1c. The tool can be inserted, and the wheel 2 fitted to the wheel seat 1c can be moved 30 mm in the axial direction, so that the flaw detection inspection by visual inspection of the wheel seat 1c is also possible.

この構成により、前記車軸１が回転すると、前記油溜め１０の潤滑油は、前記軸受３の回転に伴って前記外輪３ｂの供給孔３ｄから内輪３ａ及び転動体３ｃによって上方へ運ばれ、転動体３ｃの小径側から大径側、すなわち、軸受３の中央部分から外側へ潤滑油が流れて転動体３ｃを潤滑し、前記前蓋側環状流路部１２と前記後蓋側環状流路部１３とから前記油溜め８に循環する。この際に、上述したように、前記後蓋側環状流路部１３の容積が拡張していることから、該後蓋側環状流路部１３を流れる潤滑油が滞らず、潤滑油の温度上昇を抑えることができるとともに、スラッジの生成を少なくできる。   With this configuration, when the axle 1 rotates, the lubricating oil in the oil sump 10 is carried upward by the inner ring 3a and the rolling element 3c from the supply hole 3d of the outer ring 3b as the bearing 3 rotates, and the rolling element Lubricating oil flows from the small diameter side of 3c to the large diameter side, that is, from the central portion of the bearing 3 to the outside to lubricate the rolling element 3c, and the front lid side annular flow passage portion 12 and the rear lid side annular flow passage portion 13 are lubricated. To the oil sump 8. At this time, as described above, since the volume of the rear lid-side annular flow passage portion 13 is expanded, the lubricating oil flowing through the rear lid-side annular flow passage portion 13 does not stagnate, and the temperature of the lubricating oil rises. And the generation of sludge can be reduced.

本実施形態例では、前記軸箱４のちりよけ座側の端部４ｂを前記輪座方向へ延長するとともに、前記オイルシール９の嵌合位置及び摺接位置を前記ちりよけ座１ｂの輪座側外周に位置させたことにより、前記後蓋側環状流路部１３の容積が従来に比べて大幅に拡張し、前記前蓋側環状流路部１２と前記後蓋側環状流路部１３の容積比は、１：０．９程度となった。   In this embodiment, the end 4b of the axle box 4 on the side of the anti-slip seat is extended in the direction of the wheel seat, and the fitting position and the sliding contact position of the oil seal 9 are set on the anti-slip seat 1b. By being positioned on the outer periphery of the wheel seat side, the volume of the rear lid side annular flow passage portion 13 is greatly expanded as compared with the conventional case, and the front lid side annular flow passage portion 12 and the rear lid side annular flow passage portion 12 The volume ratio of 13 was about 1: 0.9.

本出願人が実施した台上回転試験では、時速３０５ｋｍ相当の回転数では、図９に示されるように、軸箱４の温度は、前蓋側よりも後蓋側のほうが低かった。これは、前記後蓋側環状流路部１３から前記油溜め１０へ循環する潤滑油の流量が従来より増加し、後蓋側環状流路部１３を流れる潤滑油が滞らないため、後蓋側環状流路部１３を流れる潤滑油の温度が前記前蓋側環状流路部１２を流れる潤滑油の温度よりも低いことに起因するものであることは明らかである。この検査結果から、前記前蓋側環状流路部１２と前記後蓋側環状流路部１３の容積比が１：０．７程度でも、軸箱４の温度は前蓋側と後蓋側とが略同温になると推測できる。また、前記後蓋７の輪座側端部７ｈと前記輪座１ｃに嵌合された車輪２との間に、前記軸受３を軸端方向に引き抜くための治具を挿入するスペースの確保を考慮すると、前記前蓋側環状流路部１２と前記後蓋側環状流路部１３の容積比を１：１．３程度にまで拡張可能である。   In the tabletop rotation test conducted by the present applicant, the temperature of the axle box 4 was lower on the rear lid side than on the front lid side as shown in FIG. 9 at a rotational speed corresponding to 305 km / h. This is because the flow rate of the lubricating oil circulated from the rear lid side annular flow path portion 13 to the oil sump 10 is increased from the conventional level, and the lubricating oil flowing through the rear lid side annular flow path portion 13 does not stagnate. Obviously, the temperature of the lubricating oil flowing through the annular flow passage portion 13 is lower than the temperature of the lubricating oil flowing through the front lid side annular flow passage portion 12. From this inspection result, even if the volume ratio of the front lid-side annular flow passage portion 12 and the rear lid-side annular flow passage portion 13 is about 1: 0.7, the temperature of the axle box 4 is the same between the front lid side and the rear lid side. Can be estimated to be approximately the same temperature. Further, it is possible to secure a space for inserting a jig for pulling out the bearing 3 in the axial direction between the wheel seat side end portion 7h of the rear lid 7 and the wheel 2 fitted to the wheel seat 1c. In consideration, the volume ratio of the front lid side annular flow path portion 12 and the rear lid side annular flow path portion 13 can be expanded to about 1: 1.3.

本実施形態例の車軸支持構造の拡大断面図Expanded sectional view of the axle support structure of the present embodiment example 同じく車軸の一方の支持構造を示す断面図Similarly, a sectional view showing one support structure of the axle 軸箱を軸端側から見た図View of shaft box viewed from shaft end 図３のＩＶ−ＩＶ断面図IV-IV sectional view of FIG. 軸箱を反軸端側から見た図The shaft box viewed from the opposite end 後蓋を軸端側から見た図View of rear lid viewed from shaft end 図６のＶＩＩ−ＶＩＩ断面図VII-VII sectional view of FIG. 後蓋の底面図Bottom view of rear lid 軸受の前蓋側と後蓋側の温度図Temperature diagram of the front lid side and rear lid side of the bearing 従来の車軸支持構造の拡大断面図Expanded sectional view of a conventional axle support structure

符号の説明Explanation of symbols

１…車軸、１ａ…貫通孔、１ｃ…輪座、１ｄ…ちりよけ座、１ｅ…ジャーナル、２…車輪、３…複列円錐ころ軸受、３ａ…内輪、３ｂ…外輪、３ｃ…転動体、４…軸箱、４ａ…鍔部、４ｂ…ちりよけ座側端部、４ｃ…軸端部、４ｄ…前蓋側流路部、４ｅ…第１後蓋側流路部、４ｆ…第２後蓋側流路部、４ｇ…第３後蓋側流路部、５…軸受押さえ、６…油切り、６ｄ…油切り６のオイルシール摺接位置、７…後蓋、７ａ…軸受押さえ部、７ｄ…第１切り欠き流路部、７ｅ…第２切り欠き流路部、７ｆ…第３切り欠き流路部、７ｇ…オイルシール嵌合位置、８…ラビリンスシール、９…オイルシール、９ａ…オイルシール９のリップ部、１０…油溜め、１１…前蓋、１２…前蓋側環状流路部、１３…後蓋側環状流路部   DESCRIPTION OF SYMBOLS 1 ... Axle, 1a ... Through-hole, 1c ... Wheel seat, 1d ... Dust guard seat, 1e ... Journal, 2 ... Wheel, 3 ... Double row tapered roller bearing, 3a ... Inner ring, 3b ... Outer ring, 3c ... Rolling element, 4 ... axle box, 4a ... collar, 4b ... dust guard side end, 4c ... shaft end, 4d ... front lid side channel, 4e ... first rear lid side channel, 4f ... second Rear lid side flow path section, 4g ... third rear lid side flow path section, 5 ... bearing press, 6 ... oil removal, 6d ... oil seal sliding contact position of oil drain 6, 7 ... rear cover, 7a ... bearing press section , 7d: first notch channel portion, 7e: second notch channel portion, 7f: third notch channel portion, 7g: oil seal fitting position, 8: labyrinth seal, 9 ... oil seal, 9a ... Lip part of oil seal 9, 10 ... Oil sump, 11 ... Front lid, 12 ... Front lid side annular channel, 13 ... Rear lid side annular channel

Claims (2)

輪座に車輪を嵌合した車軸を複列円錐ころ軸受を介して軸箱に支承し、前記軸受の回転時に前記軸箱の油溜めから前記軸受の転動体を油浴して油溜めに循環する潤滑油の流路を、前記軸受と前蓋との間に画成される前蓋側環状流路部と、前記軸受と後蓋に嵌合されたオイルシールとの間に画成される後蓋側環状流路部と、前記軸箱の鍔部の下部に形成した前記油溜めと前記前蓋側環状流路部とを連通する凹溝状の前蓋側流路部と、前記軸箱の後蓋側の下部に形成した前記油溜めと前記後蓋側環状流路部とを連通する凹溝状の後蓋側流路部と、前記後蓋の軸受押さえ部の下部を切り欠いて前記後蓋側流路部と前記後蓋側環状流路部とを連通する切り欠き流路部とで構成した鉄道車両において、前記軸箱の輪座側端部を前記輪座方向へ延長するとともに、前記軸箱と前記車軸のちりよけ座に固定される油切り間を塞ぐ後蓋の軸受押さえ部と輪座側端部とを前記車軸の軸線方向に延長して、前記後蓋の輪座側端部と前記油切りとの間に形成されるラビリンスシールを前記輪座に近接させ、前記後蓋の軸受押さえ部の内周面に嵌合されるオイルシールの嵌合位置と前記油切りの外周面に摺接する前記オイルシールのリップ部の摺接位置とを前記ちりよけ座の輪座側外周に位置させたことを特徴とする鉄道車両。 An axle with a wheel fitted to a wheel seat is supported by a shaft box via a double-row tapered roller bearing, and the rolling element of the bearing is oil bathed from the oil reservoir of the shaft box and circulated to the oil reservoir when the bearing rotates. The lubricating oil flow path is defined between a front lid side annular flow path portion defined between the bearing and the front lid, and an oil seal fitted to the bearing and the rear lid. A rear lid-side annular flow passage portion, a groove-shaped front lid-side flow passage portion that communicates the oil reservoir formed at the lower portion of the flange portion of the axle box and the front lid-side annular flow passage portion, and the shaft. A groove-shaped rear lid side flow passage portion that communicates the oil sump formed at the lower portion of the rear lid side of the box and the rear lid side annular flow passage portion, and a lower portion of the bearing pressing portion of the rear lid are cut out. In the railway vehicle constituted by the notch channel portion that communicates the rear lid side channel portion and the rear lid side annular channel portion, the wheel seat side end portion of the axle box is extended in the wheel seat direction. Then Further, the rear cover is formed by extending a bearing pressing portion and a wheel seat side end portion of the rear lid that closes a gap between oil drains fixed to the axle box and the dust seat of the axle in the axial direction of the axle. The labyrinth seal formed between the wheel seat side end of the wheel seat and the oil drainer is brought close to the wheel seat, and the fitting position of the oil seal fitted to the inner peripheral surface of the bearing pressing portion of the rear lid is A railway vehicle characterized in that a sliding contact position of a lip portion of the oil seal that is in sliding contact with an outer peripheral surface of the oil drainer is located on an outer periphery of the dust guard seat side. 前記前蓋側環状流路部と前記後蓋側環状流路部のそれぞれの容積を略同容積としたことを特徴とする請求項１記載の鉄道車両。 2. The railway vehicle according to claim 1, wherein the volumes of the front lid-side annular flow path portion and the rear lid-side annular flow path portion are substantially the same volume.
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WO2010018630A1 (en) * 2008-08-14 2010-02-18 三菱重工業株式会社 Wind driven electric power generator
CN103640590A (en) * 2013-12-23 2014-03-19 哈尔滨轨道交通装备有限责任公司 Rail wagon bearing device and manufacturing method thereof
JP2016026947A (en) * 2014-06-26 2016-02-18 日本車輌製造株式会社 Railroad vehicle truck with journal box structure
CN110228501A (en) * 2018-03-06 2019-09-13 斯凯孚公司 Bearing housing and the bogie for rail vehicle including this plants case
CN110228500A (en) * 2018-03-06 2019-09-13 斯凯孚公司 Bear box and the bogie for rail vehicle including this shell

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010018630A1 (en) * 2008-08-14 2010-02-18 三菱重工業株式会社 Wind driven electric power generator
JPWO2010018630A1 (en) * 2008-08-14 2012-01-26 三菱重工業株式会社 Wind power generator
CN103640590A (en) * 2013-12-23 2014-03-19 哈尔滨轨道交通装备有限责任公司 Rail wagon bearing device and manufacturing method thereof
JP2016026947A (en) * 2014-06-26 2016-02-18 日本車輌製造株式会社 Railroad vehicle truck with journal box structure
CN110228501A (en) * 2018-03-06 2019-09-13 斯凯孚公司 Bearing housing and the bogie for rail vehicle including this plants case
CN110228500A (en) * 2018-03-06 2019-09-13 斯凯孚公司 Bear box and the bogie for rail vehicle including this shell
CN110228500B (en) * 2018-03-06 2023-08-18 斯凯孚公司 Bearing housing and bogie for a rail vehicle comprising such a housing
CN110228501B (en) * 2018-03-06 2024-05-10 斯凯孚公司 Bearing housing and bogie for a rail vehicle comprising such a housing

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