JP3901874B2 - Double row tapered roller bearing device - Google Patents

Double row tapered roller bearing device Download PDF

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JP3901874B2
JP3901874B2 JP17701799A JP17701799A JP3901874B2 JP 3901874 B2 JP3901874 B2 JP 3901874B2 JP 17701799 A JP17701799 A JP 17701799A JP 17701799 A JP17701799 A JP 17701799A JP 3901874 B2 JP3901874 B2 JP 3901874B2
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ring
row
tapered roller
bearing device
raceway
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JP2000081035A (en
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浩也 柴口
陽一 沼田
宣哉 鈴木
洋司 紺野
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JFE Steel Corp
JTEKT Corp
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JFE Steel Corp
JTEKT Corp
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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
    • F16C33/46—Cages for rollers or needles
    • F16C33/52—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers
    • F16C33/523—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers
    • F16C33/526—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers extending through the rollers and joining two lateral cage parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/12—Rolling apparatus, e.g. rolling stands, rolls

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば圧延機のロールネックを支持する複列円すいころ軸受装置に関する。
【０００２】
【従来の技術】
図６は、圧延機のロールネックを回転自在に支持する従来の複列円すいころ軸受装置の一例を示す断面図である。
この複列円すいころ軸受装置は、２列の円すい状の内輪軌道２１ａを有する内輪２１と同心に、単列の円すい状の外輪軌道２２ａを有する一対の外輪２２が、その間に間座２６を介在した状態で配置されている。内輪２１は全体が一体形成されているものであり、その内周は、ロールネック２７の交換の便宜のために、当該ロールネック２７の外周にルーズに嵌合されている。また、各内輪軌道２１ａと、これに対向する各外輪軌道２２ａとの間には、転動体としての円すいころ２４を介在しており、各円すいころ２４は、保持器２５により各列毎に保持されている。
ところで、上記複列円すいころ軸受装置には、圧延時に偏荷重が負荷される場合があり、偏荷重が小さい値であっても、軸受に作用する転倒モーメントの影響が大きく、軸受寿命が短くなることがある。特に、図６に示すように偏荷重Ｒが作用する位置が、軸受の転動体荷重の作用点範囲Ｗよりも軸方向外側である場合には、軸受に反転荷重が発生し、軸受寿命が極端に短くなる。
【０００３】
そこで、図７に示す複列円すいころ軸受装置が提案されている（例えば特開平８−１８４３１３号公報参照）。この円すいころ軸受装置は、その内輪３１及び外輪３２の各軌道３１ａ，３２ａが、図において逆ハの字形に形成されているものであり、転動体荷重の作用線Ｌが外輪３２の径方向外側で交差するようになっている。また、一対の外輪３２は、それぞれ周方向の２箇所を境界として２分割されており、これにより、内輪３１の各軌道３１ａに沿って配列された円すいころ３３に対して各外輪３２を組み付け可能になっている。この軸受装置によれば、転動体荷重の作用線Ｌが一対の外輪３２の径方向外側にて交差するので、軸受に偏荷重が作用した場合でも、転倒モーメントの作用が少なく、軸受寿命の低下が防止される。
【０００４】
【発明が解決しようとする課題】
ところで、前記複列円すいころ軸受装置は、圧延機に組み込んで一定期間使用した後、外輪３２を周方向に回動させてその負荷が作用する位置をずらすことにより、繰り返し再使用することが行われている。しかし、図７に示す円すいころ軸受装置は、一対の外輪３２が周方向の２箇所を境界として２分割されているので、軸受装置を再使用する場合に、外輪３２の分割面の近傍に負荷が作用するのを避ける必要がある。このため、軸受を再使用する回数が少なくなり、軸受装置の寿命を十分に伸ばすことができないという問題があった。
本発明はかかる事情に鑑みてなされたものであり、軸受の長寿命化を図ることができる複列円すいころ軸受装置を提供することを目的とする
【０００５】
【課題を解決するための手段】
本発明に係る複列円すいころ軸受装置は、軸にルーズ状態で嵌合され、軸受中央側が小径となる円すい状の内輪軌道を一対有し、全体が一体形成された内輪と、
前記内輪と同心に配置され、前記内輪軌道に対向し且つ軸受中央側が小径となる円すい状の軌道を有し、全体が一体形成された一対の外輪と、
周方向に沿った複数箇所を境界として複数に分割され、前記一対の外輪間に介在させる外輪間座と、
外径の異なる一対のリングの相互間に複数のピンを架設し、前記外輪の端面より軸受中央側に突出するとともにその外周が円筒面とされている小径側のリングが周方向に沿った複数箇所を境界として複数に分割されたピン形保持器と、
前記ピン形保持器のピンが挿通され、前記内輪軌道とこれに対向する前記外輪軌道との間にそれぞれ介在する複数個の円すいころとを備え、
前記外輪間座の幅寸法が、その配置スペースに一方列の外輪を仮配置した状態で、保持器に組み込む一方列の円すいころが、当該外輪と干渉しないように、前記一方列の円すいころの小径側端面と前記一方列の外輪との間に隙間が形成される値に設定されていることを特徴とするものである（請求項１）。
【０００６】
この複列円すいころ軸受装置によれば、転動体荷重の作用線が外輪の径方向外側で交差するので、偏荷重が作用した場合でも転倒モーメントが作用するのを抑制することができる。また、外輪間座を組み込む前において、当該外輪間座を配置するための外輪相互間のスペースに、一方列の外輪を仮配置しておくことにより、当該一方列の内輪軌道の外方に組み込んだ保持器に、円すいころを組み込むことができ、この円すいころの組み込みが完了した後、前記スペースに仮配置した外輪を、軸方向へずらすことにより、これを各円すいころの外方に組み込むことができる。したがって、外輪が一体形成されているにもかかわらず、これを支障なく組み込むことができる。
【０００７】
前記複列円すいころ軸受装置は、保持器の小径側のリングが、互いに重ね合わせた主リングと補助リングとからなり、補助リングの外周円筒面の外径は主リングの外径よりも小さく、主リングの一側面には、補助リングの外周円筒面を嵌合してこれを主リングに調芯させるための環状の内周円筒面を備えた凹部が設けられており、これら主リング及び補助リングが、その周方向に沿った複数箇所を境界としてそれぞれ分割された複数の分割片からなるとともに、主リングと補助リングとを、それぞれの分割片の位相をずらした状態で、保持器のピンにより一体化しているのが好ましい（請求項２）。
この場合には、保持器のピンによって、主リングの分割片どうしを補助リングを介して連結することができるとともに、補助リングの分割片どうしを主リングを介して連結することができ、同時に、主リングと補助リングとを連結することができる。
【０００８】
【発明の実施の形態】
以下、本発明の実施の形態について、添付図面を参照しながら詳細に説明する。
図１に、本発明の一実施形態に係る、複列円すいころ軸受装置の断面図を示す。この複列円すいころ軸受装置は、圧延機のロールネックを支持するためのものであり、外周に円すい状の内輪軌道１ａを２列有する内輪１と、この内輪１と同心に設けられ、内周に円すい状の外輪軌道２ａをそれぞれ有する一対の外輪２と、内輪軌道１ａと外輪軌道２ａとの間に介在した転動体としての複数個の円すいころ３と、前記一対の外輪２の相互間に介在させた外輪間座４と、円すいころ３を保持する保持器５とにより構成されている。
【０００９】
内輪１は全体が一体形成されているものであり、その内周がロールネック８にルーズに嵌合されている。この内輪１の外周の両端部には、円すいころ３の大径側端面が摺接する大鍔部１ｂが設けられており、内輪軌道１ａを挟んで大鍔部１ｂに対向する位置には、円すいころ３の小径側端面が当接する小鍔部１ｃが設けられている。前記複列の内輪軌道１ａは、外輪間座４の幅寸法に対応させて所定間隔離して設けられている。
【００１０】
前記内輪軌道１ａの外径は、軸受中央側が端部側よりも小径に形成されており、外輪軌道２ａの外径は、軸受中央側が端部側よりも小径に形成されている。すなわち、各内輪軌道１ａ及び外輪軌道２ａは、転動体荷重の作用線が外輪２の径方向外側で交差するように形成されている。
【００１１】
保持器５は、外径の異なる一対の第１，第２リング５１，５２の相互間に、複数のピン５３を架設したピン形保持器である。各ピン５３は、第１リング５１のピン穴５１ａと円すいころ３の中心とを挿通しており、その挿通端は第２リング５２にねじ込まれている。前記第２リング５２は、外輪２の端面より軸受中央側に突出するとともにその外周が円筒面とされており、その外径は第１リング５１の外径よりも小さく、内径は大鍔部１ｂの外径よりも小さくなっている。
前記第２リング５２は、互いに重ね合わせた主リング５２ａと補助リング５２ｂとからなり、これら主リング５２ａ及び補助リング５２ｂは、その外周に沿った２箇所を境界として、つまり軸線を含む仮想平面Ｈ１を境界として、それぞれ２分割されているとともに（図３ａ，ｂ参照）、それぞれの側面には、ピン５３をねじ込むための複数のねじ穴ｎが等間隔に形成されている。また、補助リング５２ｂの外周円筒面の外径は主リング５２ａの外径よりも小さく、前記主リング５２ａの一側面には、補助リング５２ｂの外周円筒面を嵌合してこれを主リング５２ａに調芯させるための環状の内周円筒面を備えた凹部５２ｃが設けられている。
前記補助リング５２ｂは、その分割境界部Ｄ２を主リング５２ａの分割境界部Ｄ１に対して位相を略９０°ずらした状態で（図４参照）、前記凹部５２ｃに嵌合されており、この状態で、主リング５２ａ及び補助リング５２ｂのそれぞれのねじ穴ｎにピン５３をねじ込んである。このように、ピン５３を各リング５２ａ，５２ｂのねじ穴ｎにねじ込むことにより、主リング５２ａの分割片５２ｄどうしを、補助リング５２ｂを介して連結することができるとともに、補助リング５２ｂの分割片５２ｅどうしを、主リング５２ａを介して連結することができ、これと同時に、主リング５２ａと補助リング５２ｂとを連結することができる。したがって、連結用のフランジ等を形成することなく第２リング５２を容易に組み立てることができる。なお、ピン５３は、その頭部を第１リング５１に溶接することにより、その抜脱が阻止されている。
【００１２】
外輪間座４は、その周方向に沿った２箇所を境界として、つまり軸線を含む仮想平面Ｈ２を境界として２分割されており（図５参照）、各分割片４１，４２のそれぞれの端部に設けられたフランジ部４１ａ，４２ａどうしをボルトにより連結することにより環状に組み立てられている。この外輪間座４を配置するための一対の外輪２間のスペースは、一方列の円すいころ３を保持器５に組み込む際に、対応する外輪２を仮配置するスペースとして構成されている。すなわち、外輪間座４の幅寸法Ｗ１（図１参照）は、図２に示すように、その配置スペースに一方列の外輪２（図において右側の外輪２）を仮配置した状態で、保持器５に組み込む一方列の円すいころ３が、当該外輪２と干渉しないように、一方列の円すいころ３の小径側端面と一方列の外輪２との間に隙間Ｓが形成される値に設定されている。
なお、前記外輪間座４には、外周面から内周面に至るオイルミスト供給孔４３が、周方向に沿って所定間隔ごとに設けられている（図５参照）。
また、各外輪２の外周面には、チョック（図示せず）との隙間を密封するためのＯリング７が装着されており、各外輪２の軸方向外方には、スペーサ９が配置されている（図１参照）。
【００１３】
次に、以上の構成の複列円すいころ軸受装置の組立手順の一例について説明する。まず、図２に示すように、左列の内輪軌道１ａに沿って保持器５の第１リング５１及び第２リング５２を配置した後、両リング５１，５２の相互間に円すいころ３を導入し、この円すいころ３に第１リング５１側からピン５３を挿通するとともに、ピン５３の挿通端を第２リング５２にねじ込む。以後同様にして円すいころ３を順次保持器５に組み込む。左列の円すいころ３の組み込みが完了すると、内輪１の右端側から当該内輪１に左列用の外輪２を挿入して、外輪軌道２ａに円すいころ３を内接させる。
【００１４】
次に、内輪１の右端側から右列用の外輪２を内輪１に挿入して、当該外輪２を外輪間座４の配置スペースに仮配置する（図２破線参照）。この状態で右列の内輪軌道１ａに沿って保持器５の第１リング５１及び第２リング５２を配置し、前記と同様にして円すいころ３を保持器５に組み込む。この際、円すいころ３の小径側端面と外輪２との間に隙間Ｓがあるので、円すいころ３を外輪２と干渉することなくころ径方向から保持器５に組み込むことができる。
右列の円すいころ３の組み込みが完了すると、外輪間座４の配置スペースに仮配置した外輪２を、右側へ移動させて、その外輪軌道２ａに円すいころ３を内接させる。これにより、前記外輪２を２分割することなく定位置に組み込むことができる。次いで、互いに分離された外輪間座４の各分割片４１，４２を、一対の外輪２間にそれぞれ径方向から挿入し、各分割片４１，４２の端部のフランジ部４１ａ，４２ａどうしをボルトにより連結して、両者を一体化する。以上により複列円すいころ軸受装置の組立が完了する。
【００１５】
前記の構成の複列円すいころ軸受装置によれば、転動体荷重の作用線が外輪２の径方向外側で交差するので、軸受装置に偏荷重が作用した場合でも、転倒モーメントの作用が非常に少なく、軸受寿命が低下するのを防止することができる。また、各外輪２がそれぞれ一体形成されているので、軸受装置を一定期間使用した後、これを再使用する際に、外輪２の負荷を受ける位置を任意に選択することができる。このため、軸受装置の再使用を十分に繰り返すことができ、その長寿命化を十分に達成することができる。
この発明の複列円すいころ軸受装置は、上記実施の形態に限定されるものでなく、例えば、外輪間座４及び第２リング５２を、周方向の３ヵ所以上で分割すること等、種々の設計変更を施すことができる。
【００１６】
【発明の効果】
以上のように、請求項１記載の複列円すいころ軸受装置によれば、転動体荷重の作用線が外輪の径方向外側で交差しており、軸受装置に偏荷重が作用した場合でも、転倒モーメントの作用が非常に少ないので、その寿命低下を防止することができる。また、外輪が一体形成されているので、軸受装置を再使用する際に、外輪の負荷を受ける位置を任意に選択することができる。このため、その再使用を十分に繰り返すことができ、軸受装置の寿命を十分に確保することができる。
【００１７】
請求項２記載の前記複列円すいころ軸受装置によれば、保持器のピンによって、主リングの分割片どうしを補助リングを介して連結することができるとともに、補助リングの分割片どうしを主リングを介して連結することができ、同時に、主リングと補助リングとを連結することができる。このため、保持器の小径側のリングを容易に組み立てることができる。
【図面の簡単な説明】
【図１】本発明の一実施形態に係る複列円すいころ軸受装置を示す断面図である。
【図２】組み立て途中を示す断面図である。
【図３】保持器の第２リングを分解した状態を示す図であり、(a) は主リングの側面図、(b) は補助リングの側面図である。
【図４】保持器の第２リングを示す側面図である。
【図５】外輪間座の側面図である。
【図６】従来の複列円すいころ軸受装置を示す断面図である。
【図７】従来の他の複列円すいころ軸受装置を示す断面図である。
【符号の説明】
１ 内輪
１ａ 内輪軌道
２ 外輪
２ａ 外輪軌道
３ 円すいころ
４ 外輪間座
５ 保持器５
５１ 第１リング
５２ 第２リング
５２ａ 主リング
５２ｂ 補助リング
５２ｄ 分割片
５２ｅ 分割片
５３ ピン[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a double row tapered roller bearing device that supports, for example, a roll neck of a rolling mill.
[0002]
[Prior art]
FIG. 6 is a cross-sectional view showing an example of a conventional double row tapered roller bearing device that rotatably supports a roll neck of a rolling mill.
In this double-row tapered roller bearing device, a pair of outer rings 22 having a single-row tapered outer ring raceway 22a are disposed concentrically with an inner ring 21 having two rows of tapered inner ring raceways 21a, and a spacer 26 is interposed therebetween. It is arranged in the state. The inner ring 21 is integrally formed as a whole, and its inner periphery is loosely fitted to the outer periphery of the roll neck 27 for convenience of replacement. Further, a tapered roller 24 as a rolling element is interposed between each inner ring raceway 21a and each outer ring raceway 22a opposite thereto, and each tapered roller 24 is held in each row by a cage 25. Has been.
By the way, the double row tapered roller bearing device may be subjected to an offset load during rolling, and even if the offset load is small, the influence of the overturning moment acting on the bearing is large, and the bearing life is shortened. Sometimes. In particular, as shown in FIG. 6, when the position at which the offset load R acts is outside the bearing point W of the rolling element load of the bearing in the axial direction, a reverse load is generated in the bearing, and the bearing life is extremely short. Becomes shorter.
[0003]
Therefore, a double-row tapered roller bearing device shown in FIG. 7 has been proposed (see, for example, JP-A-8-184313). In this tapered roller bearing device, the raceways 31 a and 32 a of the inner ring 31 and the outer ring 32 are formed in a reverse C shape in the drawing, and the line of action L of the rolling element load is radially outward of the outer ring 32. It is supposed to cross at. Further, the pair of outer rings 32 is divided into two parts with two circumferential positions as boundaries, so that each outer ring 32 can be assembled to the tapered rollers 33 arranged along the respective raceways 31a of the inner ring 31. It has become. According to this bearing device, the line of action L of the rolling element load intersects on the radially outer side of the pair of outer rings 32. Therefore, even when an unbalanced load acts on the bearing, the effect of the overturning moment is small and the bearing life is reduced. Is prevented.
[0004]
[Problems to be solved by the invention]
By the way, the double-row tapered roller bearing device is incorporated into a rolling mill and used for a certain period of time, and then repeatedly reused by rotating the outer ring 32 in the circumferential direction and shifting the position where the load acts. It has been broken. However, in the tapered roller bearing device shown in FIG. 7, the pair of outer rings 32 is divided into two parts with two circumferential edges as a boundary. Therefore, when the bearing apparatus is reused, a load is placed near the split surface of the outer ring 32. Must be avoided. For this reason, the frequency | count of reusing a bearing decreases, and there existed a problem that the lifetime of a bearing apparatus could not be extended enough.
The present invention has been made in view of such circumstances, and an object thereof is to provide a double-row tapered roller bearing device capable of extending the life of the bearing.
[Means for Solving the Problems]
The double-row tapered roller bearing device according to the present invention has a pair of conical inner ring raceways that are loosely fitted to the shaft and have a small diameter on the center side of the bearing, and an inner ring that is integrally formed as a whole.
A pair of outer rings disposed concentrically with the inner ring, having a conical raceway facing the inner ring raceway and having a small diameter on the center side of the bearing, and integrally formed as a whole;
An outer ring spacer, which is divided into a plurality of boundaries along a circumferential direction and interposed between the pair of outer rings;
A plurality of pins are installed between a pair of rings having different outer diameters, and a ring on the small diameter side that protrudes toward the bearing center side from the end face of the outer ring and has a cylindrical outer surface along the circumferential direction. A pin-type cage that is divided into a plurality of boundaries as a boundary;
A plurality of tapered rollers interposed between the inner ring raceway and the outer ring raceway opposed to the inner ring raceway, the pin of the pin-type cage being inserted therethrough,
The width of the outer ring spacer is such that one row of tapered rollers incorporated in the cage does not interfere with the outer ring in a state where one row of outer rings is temporarily arranged in the arrangement space. A value is set such that a gap is formed between the end face on the small diameter side and the outer ring of the one row (Claim 1).
[0006]
According to this double-row tapered roller bearing device, since the line of action of the rolling element load intersects on the outer side in the radial direction of the outer ring, it is possible to suppress the overturning moment from acting even when an unbalanced load is applied. Also, before installing the outer ring spacer, by temporarily arranging one row of outer rings in the space between the outer rings for arranging the outer ring spacer, the outer ring spacer is incorporated outside the inner ring track of the one row. Tapered rollers can be built into the cage, and after the tapered rollers are assembled, the outer ring temporarily placed in the space is shifted in the axial direction, and this is assembled to the outside of each tapered roller. Can do. Therefore, although the outer ring is integrally formed, it can be incorporated without any trouble.
[0007]
The double-row tapered roller bearing device is composed of a main ring and an auxiliary ring in which the small-diameter side ring of the cage is overlapped with each other, and the outer diameter of the outer peripheral cylindrical surface of the auxiliary ring is smaller than the outer diameter of the main ring, One side surface of the main ring is provided with a recess having an annular inner peripheral cylindrical surface for fitting the outer peripheral cylindrical surface of the auxiliary ring and aligning it with the main ring. The ring is composed of a plurality of divided pieces each divided at a plurality of locations along the circumferential direction of the ring, and the main ring and the auxiliary ring are separated from each other by shifting the phases of the divided pieces. It is preferable that they are integrated with each other (claim 2).
In this case, the retainer pins can connect the split pieces of the main ring through the auxiliary ring, and the split pieces of the auxiliary ring can be connected through the main ring, The main ring and the auxiliary ring can be connected.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 is a sectional view of a double row tapered roller bearing device according to an embodiment of the present invention. This double-row tapered roller bearing device is for supporting the roll neck of a rolling mill, and is provided with an inner ring 1 having two rows of conical inner ring raceways 1a on the outer circumference, concentric with the inner ring 1, and an inner circumference. A pair of outer rings 2 each having a conical outer ring raceway 2a, a plurality of tapered rollers 3 as rolling elements interposed between the inner ring raceway 1a and the outer ring raceway 2a, and the pair of outer rings 2 between each other. The outer ring spacer 4 is interposed, and the cage 5 that holds the tapered rollers 3.
[0009]
The inner ring 1 is integrally formed as a whole, and its inner periphery is loosely fitted to the roll neck 8. At both ends of the outer periphery of the inner ring 1, there are provided large collar portions 1b with which the large-diameter side end surfaces of the tapered rollers 3 are slidably contacted, and at the positions facing the large collar portions 1b across the inner ring raceway 1a, A small flange portion 1c with which the end surface on the small diameter side of the roller 3 abuts is provided. The double-row inner ring raceway 1 a is provided at a predetermined interval in accordance with the width dimension of the outer ring spacer 4.
[0010]
The outer diameter of the inner ring raceway 1a is formed smaller in the bearing center side than the end side, and the outer diameter of the outer ring raceway 2a is formed smaller in the bearing center side than the end side. That is, each inner ring raceway 1 a and outer ring raceway 2 a are formed such that the line of action of the rolling element load intersects on the outer side in the radial direction of the outer ring 2.
[0011]
The cage 5 is a pin type cage in which a plurality of pins 53 are installed between a pair of first and second rings 51 and 52 having different outer diameters. Each pin 53 is inserted through the pin hole 51 a of the first ring 51 and the center of the tapered roller 3, and the insertion end is screwed into the second ring 52. The second ring 52 protrudes from the end face of the outer ring 2 toward the center of the bearing, and its outer periphery is a cylindrical surface. The outer diameter is smaller than the outer diameter of the first ring 51, and the inner diameter is a large collar. It is smaller than the outer diameter of 1b.
The second ring 52 includes a main ring 52a and an auxiliary ring 52b that are overlapped with each other, and the main ring 52a and the auxiliary ring 52b have two locations along the outer periphery as boundaries, that is, a virtual plane H1 including an axis. And a plurality of screw holes n into which the pins 53 are screwed are formed at equal intervals on each side surface. In addition, the outer diameter of the outer peripheral cylindrical surface of the auxiliary ring 52b is smaller than the outer diameter of the main ring 52a, and the outer peripheral cylindrical surface of the auxiliary ring 52b is fitted to one side surface of the main ring 52a. A concave portion 52c having an annular inner circumferential cylindrical surface for aligning with each other is provided.
The auxiliary ring 52b is fitted in the recess 52c in a state where the phase of the divisional boundary D2 is shifted by approximately 90 ° with respect to the divisional boundary D1 of the main ring 52a (see FIG. 4). Thus, the pin 53 is screwed into each screw hole n of the main ring 52a and the auxiliary ring 52b. Thus, by screwing the pin 53 into the screw holes n of the rings 52a and 52b, the divided pieces 52d of the main ring 52a can be connected to each other via the auxiliary ring 52b, and the divided pieces of the auxiliary ring 52b. 52e can be connected via the main ring 52a, and at the same time, the main ring 52a and the auxiliary ring 52b can be connected. Therefore, the second ring 52 can be easily assembled without forming a connecting flange or the like. The pin 53 is prevented from being removed by welding its head to the first ring 51.
[0012]
The outer ring spacer 4 is divided into two parts with two places along the circumferential direction as a boundary, that is, a virtual plane H2 including an axis (see FIG. 5), and the respective end portions of the divided pieces 41 and 42 The flange portions 41a and 42a provided on the ring are connected to each other by bolts, and are assembled in an annular shape. The space between the pair of outer rings 2 for arranging the outer ring spacer 4 is configured as a space for temporarily arranging the corresponding outer ring 2 when the tapered rollers 3 in one row are assembled in the cage 5. That is, as shown in FIG. 2, the width dimension W1 of the outer ring spacer 4 (see FIG. 1) is such that the outer ring 2 in one row (the outer ring 2 on the right side in the drawing) is temporarily placed in the arrangement space. 5 so that the gap S is formed between the end surface on the small-diameter side of the tapered roller 3 in one row and the outer ring 2 in one row so that the one row of tapered rollers 3 incorporated in 5 does not interfere with the outer ring 2. ing.
The outer ring spacer 4 is provided with oil mist supply holes 43 extending from the outer peripheral surface to the inner peripheral surface at predetermined intervals along the circumferential direction (see FIG. 5).
Further, an O-ring 7 for sealing a gap with a chock (not shown) is mounted on the outer peripheral surface of each outer ring 2, and a spacer 9 is disposed on the outer side in the axial direction of each outer ring 2. (See FIG. 1).
[0013]
Next, an example of the assembly procedure of the double row tapered roller bearing device having the above configuration will be described. First, as shown in FIG. 2, the first ring 51 and the second ring 52 of the cage 5 are arranged along the inner ring raceway 1 a in the left row, and then the tapered roller 3 is introduced between the rings 51 and 52. The pin 53 is inserted into the tapered roller 3 from the first ring 51 side, and the insertion end of the pin 53 is screwed into the second ring 52. Thereafter, the tapered rollers 3 are sequentially incorporated in the cage 5 in the same manner. When the incorporation of the left row tapered roller 3 is completed, the left row outer ring 2 is inserted into the inner ring 1 from the right end side of the inner ring 1, and the tapered roller 3 is inscribed in the outer ring raceway 2a.
[0014]
Next, the outer ring 2 for the right row is inserted into the inner ring 1 from the right end side of the inner ring 1, and the outer ring 2 is temporarily arranged in the arrangement space of the outer ring spacer 4 (see the broken line in FIG. 2). In this state, the first ring 51 and the second ring 52 of the cage 5 are arranged along the inner ring raceway 1a in the right row, and the tapered roller 3 is assembled in the cage 5 in the same manner as described above. At this time, since there is a gap S between the small diameter side end face of the tapered roller 3 and the outer ring 2, the tapered roller 3 can be incorporated into the cage 5 from the roller radial direction without interfering with the outer ring 2.
When the assembly of the tapered roller 3 in the right row is completed, the outer ring 2 temporarily arranged in the arrangement space of the outer ring spacer 4 is moved to the right side, and the tapered roller 3 is inscribed in the outer ring raceway 2a. Thereby, the said outer ring | wheel 2 can be integrated in a fixed position, without dividing into two. Next, the divided pieces 41 and 42 of the outer ring spacer 4 separated from each other are inserted between the pair of outer rings 2 in the radial direction, and the flange portions 41a and 42a at the ends of the divided pieces 41 and 42 are bolted to each other. To connect them together. This completes the assembly of the double row tapered roller bearing device.
[0015]
According to the double-row tapered roller bearing device having the above-described configuration, since the line of action of the rolling element load intersects on the outer side in the radial direction of the outer ring 2, even when an eccentric load is applied to the bearing device, the effect of the overturning moment is very high. Therefore, the bearing life can be prevented from decreasing. Moreover, since each outer ring | wheel 2 is each integrally formed, after using a bearing apparatus for a fixed period, when using this again, the position which receives the load of the outer ring | wheel 2 can be selected arbitrarily. For this reason, the reuse of the bearing device can be sufficiently repeated, and the life extension thereof can be sufficiently achieved.
The double-row tapered roller bearing device of the present invention is not limited to the above-described embodiment. For example, the outer ring spacer 4 and the second ring 52 may be divided into various parts such as dividing at three or more locations in the circumferential direction. Design changes can be made.
[0016]
【The invention's effect】
As described above, according to the double row tapered roller bearing device according to the first aspect, the line of action of the rolling element load intersects on the outer side in the radial direction of the outer ring, and even if an eccentric load acts on the bearing device, Since the action of the moment is very small, it is possible to prevent the lifetime from being reduced. In addition, since the outer ring is integrally formed, the position where the load on the outer ring is received can be arbitrarily selected when the bearing device is reused. For this reason, the reuse can be sufficiently repeated, and the life of the bearing device can be sufficiently ensured.
[0017]
According to the double-row tapered roller bearing device according to claim 2, the split pieces of the main ring can be connected to each other via the auxiliary ring by the pin of the cage, and the split pieces of the auxiliary ring are connected to the main ring. The main ring and the auxiliary ring can be connected at the same time. For this reason, the ring on the small diameter side of the cage can be easily assembled.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a double row tapered roller bearing device according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view showing an assembly process.
FIGS. 3A and 3B are views showing a state in which the second ring of the cage is disassembled, wherein FIG. 3A is a side view of the main ring, and FIG. 3B is a side view of the auxiliary ring.
FIG. 4 is a side view showing a second ring of the cage.
FIG. 5 is a side view of an outer ring spacer.
FIG. 6 is a cross-sectional view showing a conventional double row tapered roller bearing device.
FIG. 7 is a cross-sectional view showing another conventional double row tapered roller bearing device.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Inner ring 1a Inner ring track 2 Outer ring 2a Outer ring track 3 Tapered roller 4 Outer ring spacer 5 Cage 5
51 1st ring 52 2nd ring 52a Main ring 52b Auxiliary ring 52d Split piece 52e Split piece 53 Pin

Claims (2)

軸にルーズ状態で嵌合され、軸受中央側が小径となる円すい状の内輪軌道を一対有し、全体が一体形成された内輪と、
前記内輪と同心に配置され、前記内輪軌道に対向し且つ軸受中央側が小径となる円すい状の軌道を有し、全体が一体形成された一対の外輪と、
周方向に沿った複数箇所を境界として複数に分割され、前記一対の外輪間に介在させる外輪間座と、
外径の異なる一対のリングの相互間に複数のピンを架設し、前記外輪の端面より軸受中央側に突出するとともにその外周が円筒面とされている小径側のリングが周方向に沿った複数箇所を境界として複数に分割されたピン形保持器と、
前記ピン形保持器のピンが挿通され、前記内輪軌道とこれに対向する前記外輪軌道との間にそれぞれ介在する複数個の円すいころとを備え、
前記外輪間座の幅寸法が、その配置スペースに一方列の外輪を仮配置した状態で、保持器に組み込む一方列の円すいころが、当該外輪と干渉しないように、前記一方列の円すいころの小径側端面と前記一方列の外輪との間に隙間が形成される値に設定されていることを特徴とする複列円すいころ軸受装置。A pair of conical inner ring raceways that are loosely fitted to the shaft and have a small diameter on the center side of the bearing, and an inner ring that is integrally formed as a whole;
A pair of outer rings disposed concentrically with the inner ring, having a conical raceway facing the inner ring raceway and having a small diameter on the center side of the bearing, and integrally formed as a whole;
An outer ring spacer that is divided into a plurality of boundaries along a circumferential direction and interposed between the pair of outer rings;
A plurality of pins are installed between a pair of rings having different outer diameters, and a ring on the small diameter side that protrudes toward the bearing center side from the end face of the outer ring and has a cylindrical outer surface along the circumferential direction. A pin-type cage that is divided into a plurality of boundaries as a boundary;
A plurality of tapered rollers interposed between the inner ring raceway and the outer ring raceway opposed to the inner ring raceway, the pin of the pin-type cage being inserted therethrough,
The width of the outer ring spacer is such that one row of tapered rollers incorporated in the cage does not interfere with the outer ring in a state where one row of outer rings is temporarily arranged in the arrangement space. A double-row tapered roller bearing device, wherein a gap is formed between a small-diameter side end face and the outer ring of the one row. 前記保持器の小径側のリングが、互いに重ね合わせた主リングと補助リングとからなり、補助リングの外周円筒面の外径は主リングの外径よりも小さく、主リングの一側面には、補助リングの外周円筒面を嵌合してこれを主リングに調芯させるための環状の内周円筒面を備えた凹部が設けられており、これら主リング及び補助リングが、その周方向に沿った複数箇所を境界としてそれぞれ分割された複数の分割片からなるとともに、主リングと補助リングとを、それぞれの分割片の位相をずらした状態で、保持器のピンにより一体化している請求項１記載の複列円すいころ軸受装置。  The ring on the small diameter side of the retainer is composed of a main ring and an auxiliary ring that are overlapped with each other, and the outer diameter of the outer peripheral cylindrical surface of the auxiliary ring is smaller than the outer diameter of the main ring, A concave portion having an annular inner peripheral cylindrical surface for fitting the outer peripheral cylindrical surface of the auxiliary ring and aligning it with the main ring is provided. The main ring and the auxiliary ring are arranged along the circumferential direction. The main ring and the auxiliary ring are integrated by a pin of the cage in a state where the phases of the respective divided pieces are shifted from each other. The double row tapered roller bearing device described.
JP17701799A 1998-06-23 1999-06-23 Double row tapered roller bearing device Expired - Fee Related JP3901874B2 (en)

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JP10-175786 1998-06-23
JP17578698 1998-06-23
JP17701799A JP3901874B2 (en) 1998-06-23 1999-06-23 Double row tapered roller bearing device

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JP5125653B2 (en) * 2008-03-21 2013-01-23 株式会社ジェイテクト Tapered roller bearing, inner ring of tapered roller bearing, and method of assembling tapered roller bearing
JP5274931B2 (en) * 2008-08-12 2013-08-28 Ｎｔｎ株式会社 Double row roller bearing
CN103042038B (en) * 2013-01-10 2015-06-10 北京首钢股份有限公司 Method for prolonging service life of rolling bearing
JP2017194145A (en) * 2016-04-22 2017-10-26 Ntn株式会社 Method for assembling conical roller bearing
US10738825B2 (en) * 2018-05-08 2020-08-11 Roller Bearing Company Of America, Inc. Double row tapered roller bearing assembly having a two-piece outer ring
CN113634633B (en) * 2021-08-12 2023-03-21 中冶赛迪装备有限公司 Double-flow rolling forming device for structural steel

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