JP2012167750A - Bearing device for axle - Google Patents

Bearing device for axle Download PDF

Info

Publication number
JP2012167750A
JP2012167750A JP2011029672A JP2011029672A JP2012167750A JP 2012167750 A JP2012167750 A JP 2012167750A JP 2011029672 A JP2011029672 A JP 2011029672A JP 2011029672 A JP2011029672 A JP 2011029672A JP 2012167750 A JP2012167750 A JP 2012167750A
Authority
JP
Japan
Prior art keywords
axle
bearing device
pair
thin
inner rings
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
JP2011029672A
Other languages
Japanese (ja)
Inventor
Hiroyuki Kato
弘之 加藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JTEKT Corp
Original Assignee
JTEKT Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JTEKT Corp filed Critical JTEKT Corp
Priority to JP2011029672A priority Critical patent/JP2012167750A/en
Publication of JP2012167750A publication Critical patent/JP2012167750A/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device for an axle which more effectively prevents a stamp flaw generated in the axle.SOLUTION: A bearing device for an axle 1 includes a pair of inner rings 12, 13 arranged in an axial direction and externally fitted to an axle S, an outer ring 11 arranged on an outer peripheral side of the inner rings 12, 13 and a plurality of conical rollers 14, 15 arranged in two rows between the inner and outer rings. A pair of inner rings 12, 13 are projected from end surfaces 12c, 13c to be externally fitted to the outer peripheral surface s2 of the axle S, and provided along an axial direction with thin parts 41, 42 elastically deformable in response to the deflection of the axle S.

Description

本発明は、鉄道車両の車軸などを支持する車軸用軸受装置に関する。   The present invention relates to an axle bearing device that supports an axle or the like of a railway vehicle.

従来から、鉄道車両の車軸を回転自在に支持する車軸用軸受装置としては、複列円錐ころ軸受を構成してなるものがある。
図５は、従来の車軸用軸受装置の断面図である。図５において、車軸用軸受装置１００は、軸方向に並べて車軸１０１の端部に外嵌される一対の内輪１０２と、これら一対の内輪１０２の外周側に配置された外輪１０３と、これら内外輪１０２，１０３間に複列に配置された複数の円錐ころと１０４を備えている。
車軸１０１には、図示しない鉄道車両の車輪が一体回転可能に設けられている。上記車軸用軸受装置１００は、車軸１０１を車両に対して回転自在に支持する。 2. Description of the Related Art Conventionally, as an axle bearing device that rotatably supports an axle of a railway vehicle, there is one that constitutes a double-row tapered roller bearing.
FIG. 5 is a cross-sectional view of a conventional axle bearing device. In FIG. 5, the axle bearing device 100 includes a pair of inner rings 102 that are arranged in the axial direction and fitted onto the end of the axle 101, an outer ring 103 that is disposed on the outer peripheral side of the pair of inner rings 102, and these inner and outer rings. A plurality of tapered rollers and 104 are arranged in double rows between 102 and 103.
A wheel of a railway vehicle (not shown) is provided on the axle 101 so as to be integrally rotatable. The axle bearing device 100 supports the axle 101 so as to be rotatable with respect to the vehicle.

ここで、車軸１０１は、車両を支持しているために軸線に直交する方向に撓みが生じる。さらに、車軸１０１は、車両の走行によって回転するので、撓みが生じた状態で回転することとなり、車軸１０１と、当該車軸１０１に外嵌される内輪１０２との間で微小な滑り（フレッティング）が生じる。
特に、一対の内輪１０２が互いに対向する側の端部１０２ａには、車軸１０１の撓みによって応力が集中するため、上記フレッティングにより車軸１０１の外周面に顕著な摩耗（フレッティング摩耗）を生じさせ、車軸１０１の外周面にスタンプ傷を生じさせるおそれがあった。
上記フレッティング摩耗によるスタンプ傷は、車軸１０１の疲労破壊等の起点になる可能性があるため、その発生を防止する必要がある。 Here, since the axle 101 supports the vehicle, it bends in a direction perpendicular to the axis. Further, since the axle 101 rotates as the vehicle travels, the axle 101 rotates in a state of being bent, and a minute slip (fretting) occurs between the axle 101 and the inner ring 102 fitted on the axle 101. Occurs.
In particular, stress concentrates on the end portions 102a on the side where the pair of inner rings 102 face each other due to the bending of the axle 101. Therefore, the fretting causes remarkable wear (fretting wear) on the outer peripheral surface of the axle 101. There was a risk of causing a stamp flaw on the outer peripheral surface of the axle 101.
Since the stamp flaw due to the fretting wear may be a starting point of fatigue destruction of the axle 101, it is necessary to prevent the occurrence thereof.

そこで、車軸１０１の外周面と、内輪１０２の内周面との間に極圧添加剤を介在させて両者間の潤滑性を高めることでフレッティング摩耗を抑制し、車軸１０１の外周面にスタンプ傷が生じるのを防止するといった試みがなされている（例えば、特許文献１参照）。   Therefore, fretting wear is suppressed by interposing an extreme pressure additive between the outer peripheral surface of the axle 101 and the inner peripheral surface of the inner ring 102 to enhance the lubricity therebetween, and the outer peripheral surface of the axle 101 is stamped. Attempts have been made to prevent scratches (see, for example, Patent Document 1).

特開２００４−１１７１６号公報JP 2004-11716 A

しかし、上記従来例においても、依然として、内輪１０２の端部付近に生じる応力集中によって、車軸１０１の外周面にスタンプ傷が生じるのを十分に防止することができなかった。   However, even in the above-described conventional example, it has not been possible to sufficiently prevent a stamp scratch on the outer peripheral surface of the axle 101 due to stress concentration generated in the vicinity of the end portion of the inner ring 102.

本発明はこのような事情に鑑みてなされたものであり、車軸に生じるスタンプ傷の発生をより効果的に防止することができる車軸用軸受装置を提供することを目的とする。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide an axle bearing device that can more effectively prevent the occurrence of stamp scratches on the axle.

本発明は、軸方向に並べて車軸に外嵌される一対の内輪と、前記一対の内輪の外周外方に配置された外輪と、前記内外輪間に二列に配置された複数の転動体と、を備えた車軸用軸受装置において、前記一対の内輪の内、少なくとも一方には、前記車軸の撓みに応じて弾性変形可能な環状の薄肉部が、他方の内輪と対向する端部の内周側に設けられていることを特徴としている。   The present invention includes a pair of inner rings that are arranged in the axial direction and are externally fitted to an axle, an outer ring that is disposed on the outer periphery of the pair of inner rings, and a plurality of rolling elements that are disposed in two rows between the inner and outer rings. In at least one of the pair of inner rings, at least one of the pair of inner rings has an annular thin portion that can be elastically deformed in accordance with the deflection of the axle, and the inner circumference of the end facing the other inner ring. It is provided on the side.

上記のように構成された車軸用軸受装置によれば、内輪の端部の内周側に設けられた薄肉部が、車軸の撓みに応じて弾性変形可能であるので、当該車軸に撓みが生じたとしても、当該薄肉部は車軸の撓みに追従することができ、内輪端部における車軸の外周面に対する応力集中が生じるのを緩和することができる。これにより、フレッティング摩耗を抑制でき、車軸外周面のスタンプ傷の発生をより効果的に防止することができる。   According to the axle bearing device configured as described above, the thin portion provided on the inner peripheral side of the end portion of the inner ring can be elastically deformed in accordance with the deflection of the axle, so that the axle is bent. Even so, the thin-walled portion can follow the deflection of the axle, and the stress concentration on the outer peripheral surface of the axle at the inner ring end can be mitigated. As a result, fretting wear can be suppressed, and the occurrence of stamp flaws on the outer peripheral surface of the axle can be more effectively prevented.

上記車軸用軸受装置において、前記一対の内輪、前記外輪、及び前記転動体は、複列の円錐ころ軸受を構成しており、前記一対の内輪の内、前記車軸に一体回転可能に設けられる車輪側に位置する内輪の小鍔側の端部に前記薄肉部が設けられていることが好ましい。
この場合、車軸外周面においてスタンプ傷が特に発生し易い、車輪側に位置する内輪の小鍔側に薄肉部を設けたので、スタンプ傷の発生を一層効果的に防止することができる。 In the above-described axle bearing device, the pair of inner rings, the outer ring, and the rolling element constitute a double row tapered roller bearing, and the wheels that are provided so as to rotate integrally with the axle of the pair of inner rings. It is preferable that the thin portion is provided at the end of the inner ring located on the side on the side of the gavel.
In this case, since the thin-walled portion is provided on the small side of the inner ring located on the wheel side, where stamp scratches are particularly likely to occur on the outer peripheral surface of the axle, the occurrence of stamp scratches can be more effectively prevented.

前記薄肉部の基端部には、当該基端部に作用する応力を分散させるための凹曲面が形成されていることが好ましい。
この場合、薄肉部が車軸の撓みに応じて弾性変形する際に当該薄肉部の基端部に作用する応力を凹曲面によって分散させることができ、薄肉部の弾性変形により基端部に応力が集中するのを抑制できる。この結果、薄肉部が弾性変形することによって基端部から破損するのを防止できる。 It is preferable that a concave curved surface for dispersing stress acting on the base end portion is formed at the base end portion of the thin portion.
In this case, when the thin-walled portion is elastically deformed according to the deflection of the axle, the stress acting on the base end portion of the thin-walled portion can be dispersed by the concave curved surface, and the stress at the base end portion is caused by the elastic deformation of the thin-walled portion. Concentration can be suppressed. As a result, it is possible to prevent the thin portion from being damaged from the base end portion by elastic deformation.

本発明の車軸用軸受装置によれば、車軸に生じるスタンプ傷の発生をより効果的に防止することができる。   According to the axle bearing device of the present invention, it is possible to more effectively prevent the occurrence of stamp scratches on the axle.

本発明の第一の実施形態に係る鉄道車両の車軸用軸受装置の構成を示す断面図である。It is sectional drawing which shows the structure of the axle bearing apparatus of the railway vehicle which concerns on 1st embodiment of this invention. 内輪の小鍔部側の端面近傍を拡大した断面図である。It is sectional drawing to which the end face vicinity by the side of the small collar part of an inner ring was expanded. 本発明の第二の実施形態に係る鉄道車両の車軸用軸受装置の要部断面図である。It is principal part sectional drawing of the bearing apparatus for axles of a railway vehicle which concerns on 2nd embodiment of this invention. 本発明の第三の実施形態に係る鉄道車両の車軸用軸受装置の要部断面図である。It is principal part sectional drawing of the axle shaft bearing apparatus of the railway vehicle which concerns on 3rd embodiment of this invention. 従来の車軸用軸受装置の断面図である。It is sectional drawing of the conventional bearing apparatus for axles.

次に、本発明の好ましい実施形態について添付図面を参照しながら説明する。図１は本発明の第一の実施形態に係る鉄道車両の車軸用軸受装置の構成を示す断面図である。この車軸用軸受装置１は、鉄道車両の車軸Ｓを車体に対して回転自在に支持するものである。   Next, preferred embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 1 is a cross-sectional view showing a configuration of an axle bearing device for a railway vehicle according to a first embodiment of the present invention. The axle bearing device 1 supports an axle S of a railway vehicle so as to be rotatable with respect to a vehicle body.

図１において、車軸用軸受装置１は、車軸Ｓの端部に外嵌固定された複列の円錐ころ軸受１０を備えている。なお、車軸Ｓに一体回転可能に固定される前記鉄道車両の車輪Ｗは、車軸用軸受装置１よりも、軸方向内側に形成される取付面ｓ３に固定される。
円錐ころ軸受１０は、車両側に固定される外輪１１と、車軸Ｓに一体回転可能に固定された一対の内輪１２，１３と、これら内外輪間に転動自在かつ二列に配置された転動体としての円錐ころ１４，１５と、円錐ころ１４，１５をそれぞれ保持する保持器１６，１７とを備えている。
外輪１１は、機械構造用合金鋼や、軸受鋼等を用いて円筒状に一体的に形成された部材であり、その内周面には、一対の外輪軌道１１ａ，１１ｂが設けられている。
一対の内輪１２，１３は、機械構造用合金鋼や、軸受鋼等を用いて円筒状に形成された部材であり、軸方向に並べて車軸Ｓに外嵌固定されている。内輪１２，１３の外周面には、それぞれ、上記の外輪軌道１１ａ，１１ｂに対向する内輪軌道１２ａ，１３ａが設けられている。
外輪軌道１１ａ，１１ｂと、内輪軌道１２ａ，１３ａとの間には、上述の円錐ころ１４，１５が転動自在に配置されており、外輪１１及び内輪１２，１３は、互いに相対回転自在である。また、一対の内輪１２，１３は、互いの小鍔部１２ｂ，１３ｂ側の端部を、環状の間座１８を介在した状態で対向させて配置されている。 In FIG. 1, the axle bearing device 1 includes a double-row tapered roller bearing 10 that is externally fitted and fixed to the end portion of the axle S. The wheel W of the railway vehicle fixed to the axle S so as to be integrally rotatable is fixed to an attachment surface s3 formed on the inner side in the axial direction than the axle bearing device 1.
The tapered roller bearing 10 includes an outer ring 11 that is fixed to the vehicle side, a pair of inner rings 12 and 13 that are fixed to the axle S so as to be integrally rotatable, and a roller that is rotatable between the inner and outer rings and arranged in two rows. Tapered rollers 14 and 15 as moving bodies and retainers 16 and 17 for holding the tapered rollers 14 and 15 respectively are provided.
The outer ring 11 is a member integrally formed in a cylindrical shape using alloy steel for machine structure, bearing steel or the like, and a pair of outer ring raceways 11a and 11b are provided on the inner peripheral surface thereof.
The pair of inner rings 12 and 13 are members formed in a cylindrical shape using alloy steel for machine structure, bearing steel, or the like, and are fitted and fixed to the axle S in the axial direction. Inner ring raceways 12a and 13a facing the outer ring raceways 11a and 11b are provided on the outer peripheral surfaces of the inner races 12 and 13, respectively.
The above-mentioned tapered rollers 14 and 15 are rotatably arranged between the outer ring raceways 11a and 11b and the inner ring raceways 12a and 13a, and the outer ring 11 and the inner rings 12 and 13 are rotatable relative to each other. . Further, the pair of inner rings 12 and 13 are arranged with their end portions on the side of the small flange portions 12b and 13b facing each other with an annular spacer 18 interposed therebetween.

車軸用軸受装置１は、円錐ころ軸受１０の両端を密封する一対の密封装置２０をさらに備えている。この密封装置２０は、外輪１１の軸方向両端に固定されており、内外輪１１，１２，１３間を密封するためのシール部材２１と、このシール部材２１を外輪１１の軸方向外側で保持するシールケース２２とを備えている。
シールケース２２は、例えば、ＳＰＣＣ等の冷延鋼板をプレス加工することによって形成された環状の部材であり、外輪１１の肩部１１ｃの内周面に圧入されている。
シール部材２１は、後述する車軸Ｓに外嵌固定された環状部材３０（３１）の外周面に摺接するシールリップ（図示せず）を有している。シール部材２１は、前記シールリップによって、外輪１１に圧入固定されたシールケース２２と、環状部材３０（３１）の外周面との間を密封し、内輪１２，１３と外輪１１との間の環状開口を密封している。 The axle bearing device 1 further includes a pair of sealing devices 20 that seal both ends of the tapered roller bearing 10. The sealing device 20 is fixed to both ends in the axial direction of the outer ring 11, and a seal member 21 for sealing between the inner and outer rings 11, 12, and 13, and the seal member 21 is held on the outer side in the axial direction of the outer ring 11. And a seal case 22.
The seal case 22 is an annular member formed by pressing a cold-rolled steel plate such as SPCC, and is press-fitted into the inner peripheral surface of the shoulder 11c of the outer ring 11.
The seal member 21 has a seal lip (not shown) that comes into sliding contact with the outer peripheral surface of an annular member 30 (31) that is externally fitted and fixed to an axle S that will be described later. The seal member 21 seals between the seal case 22 press-fitted and fixed to the outer ring 11 by the seal lip and the outer peripheral surface of the annular member 30 (31), and the ring between the inner rings 12, 13 and the outer ring 11 is sealed. The opening is sealed.

車軸用軸受装置１の両端には、車軸Ｓに一体回転可能に外嵌固定された上述の環状部材３０，３１が配置されている。環状部材３０，３１は、互いに突き合わされた内輪１２，１３を軸方向両側から挟持するように車軸Ｓに外嵌固定されている。
車軸Ｓの基端部側に配置されている環状部材３１は、車軸Ｓに形成されている段部ｓ１に当接しており、軸方向基端側への移動が規制されている。さらに、車軸Ｓの先端部には、ボルト３２によって固定された蓋部材３３が配置されている。この蓋部材３３は、車軸Ｓの先端部側に配置された環状部材３０に当接して配置されており、車軸用軸受装置１の内輪１２，１３、及びその両端に配置された環状部材３０，３１を車軸Ｓの段部ｓ１との間で挟持し、車軸用軸受装置１の軸方向位置を保持している。
また、この環状部材３０，３１には、それぞれ、径外方向に突出した凸部３０ａ，３１ａが形成されている。この凸部３０ａ，３１ａには、それぞれ、シールケース２２の先端２２ａが挿入される環状溝が形成されている。この環状溝と、これに挿入されるシールケース２２の先端２２ａとは、ラビリンスシールを構成しており、シールケース２２と、環状部材３０，３１との間の密封性をより高めている。 At the both ends of the axle bearing device 1, the above-described annular members 30 and 31 that are externally fitted and fixed to the axle S so as to be integrally rotatable are disposed. The annular members 30 and 31 are externally fixed to the axle shaft S so as to sandwich the inner rings 12 and 13 that are abutted against each other from both sides in the axial direction.
The annular member 31 disposed on the base end side of the axle S is in contact with a step s1 formed on the axle S, and movement to the base end side in the axial direction is restricted. Furthermore, a lid member 33 fixed by a bolt 32 is disposed at the tip of the axle shaft S. The lid member 33 is disposed in contact with the annular member 30 disposed on the tip end side of the axle S, and the inner rings 12 and 13 of the axle bearing device 1 and the annular members 30 disposed at both ends thereof. 31 is held between the step S1 of the axle S and the axial position of the axle bearing device 1 is held.
Further, the annular members 30 and 31 are respectively formed with convex portions 30a and 31a protruding in the radially outward direction. Each of the convex portions 30a and 31a is formed with an annular groove into which the tip 22a of the seal case 22 is inserted. The annular groove and the tip 22a of the seal case 22 inserted therein constitute a labyrinth seal, which further enhances the sealing performance between the seal case 22 and the annular members 30 and 31.

図２は、内輪１２，１３の小鍔部１２ｂ，１３ｂ側の端部近傍を拡大した断面図である。図２に示すように、互いに対向する内輪１２，１３の小鍔部１２ｂ，１３ｂ側の端部内周側には、端面１２ｃ，１３ｃから突出している環状の薄肉部４１，４２が軸方向に沿って設けられている。
以下、これら薄肉部４１，４２は、同様の構成なので内輪１３の端部側に着目して説明する。
薄肉部４２は、軸方向の断面がほぼ矩形状であり、その内周面４２ａが内輪１３の内周面と面一に形成されて車軸Ｓの外周面ｓ２に外嵌している。また、薄肉部４２は、径方向の厚み寸法が、車軸Ｓに生じる軸方向に直交する方向の撓み量に対して弾性変形可能な程度に内輪１３に対して薄肉に設定されている。より具体的に、内輪１２，１３の内径が、１２０ｍｍの場合、薄肉部４２の径方向の厚みは２〜３ｍｍ、軸方向寸法は５ｍｍ程度に設定されている。 FIG. 2 is an enlarged cross-sectional view of the vicinity of the end portions of the inner rings 12 and 13 on the side of the small flange portions 12b and 13b. As shown in FIG. 2, annular thin portions 41, 42 projecting from the end surfaces 12 c, 13 c are provided along the axial direction on the inner peripheral side of the end portions of the inner rings 12, 13 facing each other on the small flange portions 12 b, 13 b side. Is provided.
Hereinafter, since these thin parts 41 and 42 are the same structures, it demonstrates paying attention to the edge part side of the inner ring | wheel 13.
The thin-walled portion 42 has a substantially rectangular cross section in the axial direction, and its inner peripheral surface 42 a is formed flush with the inner peripheral surface of the inner ring 13 and is externally fitted to the outer peripheral surface s 2 of the axle S. Further, the thin portion 42 is set to be thin with respect to the inner ring 13 such that the thickness dimension in the radial direction can be elastically deformed with respect to the bending amount in the direction orthogonal to the axial direction generated in the axle S. More specifically, when the inner diameters of the inner rings 12 and 13 are 120 mm, the thickness of the thin portion 42 in the radial direction is set to 2 to 3 mm, and the axial dimension is set to about 5 mm.

内輪１２，１３の間に介在している間座１８は、その軸方向両端にそれぞれ内輪１２，１３の端面１２ｃ，１３ｃに当接している当接面５１ａを有する環状部５１と、環状部５１の内周面５１ｂから径方向内側に突出して車軸Ｓの外周面ｓ２に外嵌している突出部５２とを備えている。
間座１８は、突出部５２の端面５２ａと、薄肉部４２の先端面４２ｂとの間、及び、環状部５１の内周面５１ｂと、薄肉部４２の外周面４２ｃとの間において、所定の隙間が形成される寸法に設定されている。従って、間座１８は、薄肉部４２に対して接触することなく、内輪１２，１３の間に介在している。よって、薄肉部４２は、車軸Ｓが軸方向に直交する方向に撓むことで弾性変形しようとしたときに、間座１８によってその変形が規制されることがない。このように、薄肉部４２は、車軸Ｓの撓みに応じて弾性変形可能とされている。 The spacer 18 interposed between the inner rings 12 and 13 has an annular portion 51 having an abutment surface 51a abutting against the end faces 12c and 13c of the inner rings 12 and 13 at both axial ends thereof, and the annular portion 51, respectively. And a protruding portion 52 that protrudes radially inward from the inner peripheral surface 51b and is fitted on the outer peripheral surface s2 of the axle S.
The spacer 18 has a predetermined space between the end surface 52a of the protruding portion 52 and the tip surface 42b of the thin portion 42, and between the inner peripheral surface 51b of the annular portion 51 and the outer peripheral surface 42c of the thin portion 42. The dimension is set so that a gap is formed. Therefore, the spacer 18 is interposed between the inner rings 12 and 13 without contacting the thin portion 42. Therefore, the thin portion 42 is not restricted by the spacer 18 when the axle shaft S is about to be elastically deformed by bending in the direction orthogonal to the axial direction. Thus, the thin portion 42 can be elastically deformed according to the bending of the axle shaft S.

薄肉部４２は、車軸Ｓの撓みに応じて弾性変形可能であるので、その内周面４２ａは、撓んだ状態で回転する車軸Ｓの外周面ｓ２に対して追従し、面接触の状態を維持することができる。この結果、薄肉部４２の内周側端縁４２ａ１が径方向内側に押圧される応力が過大になるのを抑制することができ、この内周側端縁４２ａ１近傍に応力集中が生じるのを緩和することができる。   Since the thin-walled portion 42 can be elastically deformed in response to the deflection of the axle shaft S, the inner circumferential surface 42a follows the outer circumferential surface s2 of the axle shaft S that rotates in a bent state, and changes the state of surface contact. Can be maintained. As a result, it is possible to suppress the stress that the inner peripheral side edge 42a1 of the thin wall portion 42 is pressed radially inward from being excessive, and to reduce the stress concentration in the vicinity of the inner peripheral side edge 42a1. can do.

すなわち、上記のように構成された車軸用軸受装置１によれば、内輪１３（１２）の小鍔部側の端部の内周側に設けられた薄肉部４２（４１）が、車軸Ｓの撓みに応じて弾性変形可能であるので、当該車軸Ｓに撓みが生じたとしても、薄肉部４２（４１）は車軸Ｓの撓みに追従することができ、内輪１３（１２）の端部における車軸Ｓの外周面ｓ２に対する応力集中が生じるのを緩和することができる。これにより、フレッティング摩耗を抑制でき、車軸Ｓの外周面ｓ２のスタンプ傷の発生をより効果的に防止することができる。   That is, according to the axle bearing device 1 configured as described above, the thin-walled portion 42 (41) provided on the inner peripheral side of the end portion of the inner ring 13 (12) on the small collar side is provided on the axle S. Since it can be elastically deformed according to the bending, even if the axle S is bent, the thin portion 42 (41) can follow the bending of the axle S, and the axle at the end of the inner ring 13 (12). The stress concentration on the outer peripheral surface s2 of S can be alleviated. As a result, fretting wear can be suppressed, and the occurrence of stamp flaws on the outer peripheral surface s2 of the axle S can be more effectively prevented.

図３は、本発明の第二の実施形態に係る鉄道車両の車軸用軸受装置１の要部断面図である。本実施形態では、内輪１２，１３の小鍔部１２ｂ，１３ｂ側の端部の薄肉部４１，４２は、端面１２ｃ，１３ｃから軸方向に凹む凹部１２ｄ，１３ｄを形成することで形成されている。以下、内輪１３側に着目して説明する。
凹部１３ｄは、薄肉部４２の外周面４２ｃと、端面１３ｃの内周側端縁から軸方向大径端側に向かって縮径するように傾斜するテーパ面１３ｃ２とを含んで構成されている。凹部１３ｄは、軸方向からみて、内輪軌道１３ａの位置に到達しない程度の位置まで凹むように形成されている。つまり、凹部１３ｄは、軸方向からみて、内輪軌道１３ａと重ならないように形成されている。 FIG. 3 is a cross-sectional view of a main part of the axle bearing device 1 for a railway vehicle according to the second embodiment of the present invention. In the present embodiment, the thin portions 41 and 42 at the ends of the inner races 12 and 13 on the side of the small flange portions 12b and 13b are formed by forming concave portions 12d and 13d that are recessed in the axial direction from the end surfaces 12c and 13c. . Hereinafter, description will be given focusing on the inner ring 13 side.
The recess 13d includes an outer peripheral surface 42c of the thin-walled portion 42 and a tapered surface 13c2 that is inclined so as to decrease in diameter from the inner peripheral side end edge of the end surface 13c toward the large-diameter end side in the axial direction. The recess 13d is formed to be recessed to a position that does not reach the position of the inner ring raceway 13a when viewed from the axial direction. That is, the recess 13d is formed so as not to overlap the inner ring raceway 13a when viewed from the axial direction.

また、薄肉部４２の基端部である、テーパ面１３ｃ２と、薄肉部４２の外周面４２ｃとの境界部には、両面１３ｃ２，４２ｃを繋ぐ凹曲面部５０が形成されている。
内輪１３の端部内周面側に設けられた薄肉部４２の先端面４２ｂは、内輪１３の端面１３ｃに対して、軸方向に間座１８側に突出する寸法で形成されている。 A concave curved surface portion 50 that connects both surfaces 13c2 and 42c is formed at a boundary portion between the tapered surface 13c2 and the outer peripheral surface 42c of the thin portion 42, which is the base end portion of the thin portion 42.
The distal end surface 42b of the thin portion 42 provided on the inner peripheral surface side of the end portion of the inner ring 13 is formed with a dimension that protrudes toward the spacer 18 in the axial direction with respect to the end surface 13c of the inner ring 13.

間座１８は、その端面が、内輪１３の端面１３ｃに当接する当接面１８ａと、当接面１８ａの端縁から間座１８の軸方向中心に向かって縮径するように傾斜するテーパ面１８ｂとを有している。
間座１８は、テーパ面１８ｂによって、内輪１３の当接面１３ｃ１よりも間座１８側に突出して形成されている薄肉部４２に接触することなく、内輪１２，１３の間に介在している。よって、本実施形態においても、薄肉部４２は、車軸Ｓが撓むことで弾性変形しようとしたときに、間座１８によってその変形が規制されることがなく、薄肉部４２は、車軸Ｓの撓みに応じて弾性変形可能とされている。 The spacer 18 has an abutment surface 18 a that abuts the end surface 13 c of the inner ring 13, and a tapered surface that is inclined so that the diameter of the spacer 18 decreases from the edge of the abutment surface 18 a toward the axial center of the spacer 18. 18b.
The spacer 18 is interposed between the inner rings 12 and 13 by the taper surface 18b without contacting the thin portion 42 formed to protrude toward the spacer 18 from the contact surface 13c1 of the inner ring 13. . Therefore, also in this embodiment, the thin-walled portion 42 is not restricted by the spacer 18 when the axle S is about to be elastically deformed as the axle S bends. It can be elastically deformed according to the bending.

このため、本実施形態によれば、上記第一の実施形態と同様、内輪１２，１３の端部における車軸Ｓの外周面ｓ２に対する応力集中が生じるのを緩和でき、フレッティング摩耗を抑制することができる。この結果、車軸Ｓの外周面ｓ２のスタンプ傷の発生をより効果的に防止することができる。   For this reason, according to the present embodiment, as in the first embodiment, stress concentration on the outer peripheral surface s2 of the axle S at the ends of the inner rings 12 and 13 can be alleviated, and fretting wear is suppressed. Can do. As a result, it is possible to more effectively prevent the occurrence of stamp scratches on the outer peripheral surface s2 of the axle shaft S.

また、本実施形態では、薄肉部４２の基端部には、テーパ面１３ｃ２と、薄肉部４２の外周面４２ｃとを繋ぐ凹曲面部５０が形成されているので、薄肉部４２が車軸Ｓの撓みに応じて弾性変形する際に当該薄肉部４２の基端部に作用する応力を凹曲面部５０によって分散させることができる。この結果、薄肉部４２（４１）の弾性変形により前記基端部に応力が集中するのを抑制でき、薄肉部４２（４１）が弾性変形することによって前記基端部から破損するのを防止できる。   In the present embodiment, since the concave surface portion 50 that connects the tapered surface 13c2 and the outer peripheral surface 42c of the thin portion 42 is formed at the base end portion of the thin portion 42, the thin portion 42 of the axle S is formed. The stress acting on the base end portion of the thin portion 42 when elastically deforming according to the bending can be dispersed by the concave curved surface portion 50. As a result, it is possible to suppress stress from being concentrated on the base end portion due to elastic deformation of the thin portion 42 (41), and it is possible to prevent the thin portion 42 (41) from being damaged from the base end portion due to elastic deformation. .

図４は、本発明の第三の実施形態に係る鉄道車両の車軸用軸受装置１の要部断面図である。本実施形態では、間座１８を備えておらず、内輪１２，１３が互いに突き合わされて直接当接している点で、上記各実施形態と相違している。
本実施形態の車軸用軸受装置１の内輪１２，１３において、互いに対向する端面１２ｃ，１３ｃは、互いに突き合わされて当接している。
薄肉部４１，４２は、上記第二の実施形態と同様、端面１２ｃ，１３ｃから軸方向に凹む凹部１２ｄ，１３ｄを形成することで形成されている。以下、内輪１３側に着目して説明する。
凹部１３ｄは、端面１３ｃの内周端縁から軸方向大径端側に延びる内周面１３ｃ３と、内周面１３ｃ３の端縁から径方向内側に延びる環状壁１３ｃ４と、薄肉部４２の外周面４２ｃを含んで構成されている。凹部１３ｄは、軸方向からみて、内輪軌道１３ａの位置に到達しない程度の位置まで凹むように形成されている。つまり、凹部１３ｄは、軸方向からみて、内輪軌道１３ａと重ならないように形成されている。 FIG. 4 is a cross-sectional view of a main part of the axle bearing device 1 for a railway vehicle according to the third embodiment of the present invention. This embodiment is different from each of the above embodiments in that the spacer 18 is not provided and the inner rings 12 and 13 are abutted against each other and are in direct contact with each other.
In the inner rings 12 and 13 of the axle bearing device 1 of the present embodiment, the end faces 12c and 13c facing each other are abutted against each other.
The thin portions 41 and 42 are formed by forming concave portions 12d and 13d that are recessed in the axial direction from the end surfaces 12c and 13c, as in the second embodiment. Hereinafter, description will be given focusing on the inner ring 13 side.
The recessed portion 13d includes an inner peripheral surface 13c3 extending from the inner peripheral edge of the end surface 13c toward the large-diameter end, an annular wall 13c4 extending radially inward from the end of the inner peripheral surface 13c3, and the outer peripheral surface of the thin portion 42. 42c is comprised. The recess 13d is formed to be recessed to a position that does not reach the position of the inner ring raceway 13a when viewed from the axial direction. That is, the recess 13d is formed so as not to overlap the inner ring raceway 13a when viewed from the axial direction.

薄肉部４２の基端部には、上記第二の実施形態と同様、環状壁１３ｃ４と、薄肉部４２の外周面４２ｃとを繋ぐ凹曲面部５０が形成されている。
薄肉部４２の先端面４２ｂは、内輪１３の端面１３ｃに対して軸方向に突出しない寸法に形成されている。
従って、本実施形態のように、一対の内輪の間に間座を配置しない構成においても、薄肉部４２（４１）は、車軸Ｓが撓むことで弾性変形しようとしたときに、他の部材によってその変形が規制されることがなく、薄肉部４２（４１）は、車軸Ｓの撓みに応じて弾性変形可能とされている。この結果、上記各実施形態と同様車軸Ｓの外周面ｓ２のスタンプ傷の発生をより効果的に防止することができる。 A concave curved surface portion 50 that connects the annular wall 13c4 and the outer peripheral surface 42c of the thin portion 42 is formed at the base end portion of the thin portion 42, as in the second embodiment.
The distal end surface 42 b of the thin wall portion 42 is formed to have a dimension that does not protrude in the axial direction with respect to the end surface 13 c of the inner ring 13.
Therefore, even in the configuration in which the spacer is not disposed between the pair of inner rings as in the present embodiment, the thin-walled portion 42 (41) has another member when the axle S is about to be elastically deformed by bending. Therefore, the thin portion 42 (41) can be elastically deformed according to the bending of the axle shaft S. As a result, it is possible to more effectively prevent the occurrence of stamp scratches on the outer peripheral surface s2 of the axle shaft S as in the above embodiments.

なお、本発明は、上記各実施形態に限定されるものではない。上記実施形態では、一対の内輪１２，１３の小鍔部１２ｂ，１３ｂ側に薄肉部４１，４２を形成した場合を例示したが、内輪１２，１３の内、少なくともいずれか一方に薄肉部を設けることもできる。
この場合、特に、車軸Ｓ外周面においてスタンプ傷が特に発生し易い、車輪Ｗ側に位置する内輪１３の小鍔部１３ｂ側の端部に薄肉部を設けることが好ましい。これにより、スタンプ傷の発生を一層効果的に防止することができる。
また、内輪１２，１３の大鍔部側に同様の薄肉部を設けてもよい。 The present invention is not limited to the above embodiments. In the above embodiment, the case where the thin portions 41 and 42 are formed on the small flange portions 12b and 13b side of the pair of inner rings 12 and 13 is illustrated. However, at least one of the inner rings 12 and 13 is provided with the thin portion. You can also
In this case, in particular, it is preferable to provide a thin portion at the end of the inner ring 13 on the wheel W side where the stamp S is particularly likely to be generated on the outer peripheral surface of the axle shaft S. Thereby, generation | occurrence | production of a stamp damage | wound can be prevented more effectively.
Moreover, you may provide the same thin part in the large collar part side of the inner rings 12 and 13. FIG.

また、上記実施形態では、薄肉部４１が、軸方向断面がほぼ矩形状に形成した場合を例示したが、車軸Ｓの外周面ｓ２に外嵌し車軸Ｓの撓みに応じて弾性変形可能に薄肉に形成されていれば、矩形以外の異形形状とすることもできる。   Moreover, in the said embodiment, although the case where the thin part 41 formed the axial direction cross section in the substantially rectangular shape was illustrated, it is fitted thinly on the outer peripheral surface s2 of the axle shaft S, and is thin-walled so that it can be elastically deformed according to the bending of the axle shaft S If it is formed in, it can also be made into irregular shapes other than a rectangle.

また、上記各実施形態では、鉄道車両の車軸を支持する車軸用軸受装置に、本発明を適用した場合を例示したが、自動車等鉄道以外の車両の車軸を支持する軸受装置に適用することもできる。また、上記各実施形態では、複列の円錐ころ軸受を構成する軸受装置に本発明を適用した場合を示したが、複列の円筒ころ軸受や、アンギュラ玉軸受等についても同様に適用することができる。   Further, in each of the above embodiments, the case where the present invention is applied to an axle bearing device that supports an axle of a railway vehicle is illustrated, but the present invention may also be applied to a bearing device that supports an axle of a vehicle other than a railway such as an automobile. it can. In each of the above embodiments, the case where the present invention is applied to a bearing device that constitutes a double-row tapered roller bearing has been shown, but the same applies to a double-row cylindrical roller bearing, an angular ball bearing, and the like. Can do.

１：車軸用軸受装置 １１：外輪 １２，１３：内輪
１２ｃ，１３ｃ：端面（軸方向端面） １４，１５：円錐ころ（転動体）
４１，４２：薄肉部 ５０：凹曲面部 Ｓ：車軸 ｓ２：外周面
Ｗ：車輪 1: Bearing device for axle 11: Outer ring 12, 13: Inner ring 12c, 13c: End face (end face in the axial direction) 14, 15: Tapered roller (rolling element)
41, 42: Thin portion 50: Concave surface portion S: Axle s2: Outer peripheral surface W: Wheel

Claims (3)

軸方向に並べて車軸に外嵌される一対の内輪と、
前記一対の内輪の外周外方に配置された外輪と、
前記内外輪間に二列に配置された複数の転動体と、を備えた車軸用軸受装置において、
前記一対の内輪の内、少なくとも一方には、前記車軸の撓みに応じて弾性変形可能な環状の薄肉部が、他方の内輪と対向する端部の内周側に設けられていることを特徴とする車軸用軸受装置。 A pair of inner rings that are axially aligned and fitted to the axle;
An outer ring disposed on the outer periphery of the pair of inner rings;
A plurality of rolling elements arranged in two rows between the inner and outer rings, and an axle bearing device comprising:
At least one of the pair of inner rings is provided with an annular thin portion that is elastically deformable according to the deflection of the axle on the inner peripheral side of the end facing the other inner ring. Axle bearing device. 前記一対の内輪、前記外輪、及び前記転動体は、複列の円錐ころ軸受を構成しており、
前記一対の内輪の内、前記車軸に一体回転可能に設けられる車輪側に位置する内輪の小鍔側の端部に前記薄肉部が設けられている請求項１に記載の車軸用軸受装置。 The pair of inner rings, the outer ring, and the rolling elements constitute double-row tapered roller bearings,
2. The axle bearing device according to claim 1, wherein, in the pair of inner rings, the thin-walled portion is provided at an end of the inner ring located on a wheel side that is provided on the axle so as to be integrally rotatable with the axle. 前記薄肉部の基端部には、当該基端部に作用する応力を分散させるための凹曲面が形成されている請求項１又は２に記載の車軸用軸受装置。   The axle bearing device according to claim 1 or 2, wherein a concave curved surface for dispersing stress acting on the base end portion is formed at a base end portion of the thin portion.
JP2011029672A 2011-02-15 2011-02-15 Bearing device for axle Withdrawn JP2012167750A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2011029672A JP2012167750A (en) 2011-02-15 2011-02-15 Bearing device for axle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011029672A JP2012167750A (en) 2011-02-15 2011-02-15 Bearing device for axle

Publications (1)

Publication Number Publication Date
JP2012167750A true JP2012167750A (en) 2012-09-06

Family

ID=46972097

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2011029672A Withdrawn JP2012167750A (en) 2011-02-15 2011-02-15 Bearing device for axle

Country Status (1)

Country Link
JP (1) JP2012167750A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013068275A (en) * 2011-09-22 2013-04-18 Ntn Corp Double row tapered roller bearing
JP2015007442A (en) * 2013-06-25 2015-01-15 株式会社不二越 Bearing seal, bearing, and vehicular bearing device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013068275A (en) * 2011-09-22 2013-04-18 Ntn Corp Double row tapered roller bearing
JP2015007442A (en) * 2013-06-25 2015-01-15 株式会社不二越 Bearing seal, bearing, and vehicular bearing device

Similar Documents

Publication Publication Date Title
US20100189387A1 (en) Rolling bearing
JP5911688B2 (en) Double row tapered roller bearing
JP2012241824A (en) Bearing unit with packing seal
JP2015152030A (en) Sealing device and vehicle bearing device with the same
JP2012112494A (en) Sealing device of wheel bearing
WO2014058038A1 (en) Bearing device
JP6114556B2 (en) Wheel bearing device
JP2012167750A (en) Bearing device for axle
JP6309228B2 (en) Manufacturing method of wheel bearing device
JP2020020351A (en) Wheel support rolling bearing unit
JP5056116B2 (en) Rolling bearing device
JP6396681B2 (en) Wheel bearing device
JP5132457B2 (en) Double row tapered roller bearing
JP6649611B2 (en) Bearing device
JP2019044915A (en) Bearing device for wheel
US7614794B2 (en) Rolling bearing device
JP2005106070A (en) Roller bearing
JP4731198B2 (en) Roller bearing
JP4905222B2 (en) Rolling bearing device
JP2005163828A (en) Bearing device
JP6662135B2 (en) Rolling bearing device
JP2008249040A (en) Rolling bearing device
JP4731508B2 (en) Double row tapered roller bearing
JP4991619B2 (en) Rolling bearing device
JP2007154950A (en) Bearing device for wheel

Legal Events

Date Code Title Description
A300 Withdrawal of application because of no request for examination

Free format text: JAPANESE INTERMEDIATE CODE: A300

Effective date: 20140513