JP3646951B2 - Sealed roller bearings in rolling mills. - Google Patents

Sealed roller bearings in rolling mills. Download PDF

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Publication number
JP3646951B2
JP3646951B2 JP26027196A JP26027196A JP3646951B2 JP 3646951 B2 JP3646951 B2 JP 3646951B2 JP 26027196 A JP26027196 A JP 26027196A JP 26027196 A JP26027196 A JP 26027196A JP 3646951 B2 JP3646951 B2 JP 3646951B2
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Japan
Prior art keywords
outer ring
ring body
inner ring
flanges
sliding contact
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JP26027196A
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Japanese (ja)
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JPH1085809A (en
Inventor
宣哉 鈴木
和也 藤本
豊 若島
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Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/388—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 four rows, i.e. four row tapered roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • 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)

Description

【０００１】
【発明の属する技術分野】
この発明は、圧延機における密封形ころ軸受に関する。
【０００２】
【従来の技術】
従来、圧延機における密封形ころ軸受としては、図４および図５に示す特公平３−６６９６３号公報のものが知られている。この従来軸受４０は、圧延機のロールネック４１を軸箱５４内に支承する４列円すいころ軸受である。軸受４０の両端部において、内輪４２の小鍔側に外輪４３の端面よりも軸方向に延長する延長環体部４２ａが形成され、この延長環体部４２ａに、外向きフランジ４４ａ，４５ａ，４６ａをそれぞれ有する３個の内側環体４４，４５，４６が軸方向へ重合して連結された状態で外嵌されている。また、外輪４３の端面側に、内向きフランジ４７ａ，４８ａをそれぞれ有する２個の外側環体４７，４８が、内側環体４４，４５，４６と同心状に軸方向へ重合して連結された状態で位置させられている。上記複数の外向きフランジ４４ａ，４５ａ，４６ａと複数の内向きフランジ４７ａ，４８ａは、軸方向両端部に外向きフランジ４４ａ，４４ｃが位置して交互に並列するように配列されている。このようにして、内側環体４４，４５，４６の外周部と外側環体４７，４８の内周部の間にラビリンス４９が形成され、非接触密封装置５０が構成されている。
【０００３】
また、上記３個の内側環体４４，４５，４６のうち、最も軸受内部に近い内側環体４４が内輪２２の延長環体部４２ａに焼嵌めにて固着され、他の内側環体４５，４６は分離可能なようにねじ５１にて内側環体４４と締結固定されている。さらに２個の外側環体４７，４８は分離可能なようにねじ５２にて締結され、軸受内部側の外側環体４７と外輪４３とは外輪４３の端面と着脱自在にインロウ結合されている。なお５３はＯリングで、外側環体４７の外周部に形成した周溝５５に嵌合されて、軸箱５４の内周面と外側環体４７の外周面を密封する。また、５５は内・外輪間に介装された円すいころである。
【０００４】
【発明が解決しようとする課題】
しかしながら、上記の軸受４０においては、圧延機の高速回転時には、非接触密封装置５０に強力なエアカーテンが作り出され、圧延機に使用される冷却水や塵埃の軸受４０内部への侵入が防止され、高い密封性能が得られる。しかし、ラビリンス構成であるため、圧延機の運転停止時に非接触密封装置５０内に溜まった水等が、運転開始時にラビリンスを伝わって軸受４０内部に侵入する恐れがある。さらに、圧延スケジュールにより圧延機が低速運転となった場合にも、非接触密封装置５０のエアカーテンが弱いため、軸受４０内部に水等が侵入する恐れがある。
【０００５】
そこで、この発明の目的は、圧延機の運転停止時や低速回転時に、軸受内部へ水等の侵入を防止する圧延機における密封形ころ軸受を提供することにある。
【０００６】
【課題を解決するための手段】
上記課題を解決するための手段として、内輪の端部に、外向きフランジを有する複数の内側環体を軸方向に重合して配列し、外輪の端部に、内向きフランジを有する複数の外側環体を軸方向に重合しかつ内側環体と同心状に配列し、外向きフランジが軸方向両端部に位置するよう外向きフランジと内向きフランジとを交互に配列してこれらフランジ間の隙間によりラビリンスとされた密封空間を形成した圧延機における密封形ころ軸受において、二つの隣接する上記外側環体の内向きフランジ間に位置する上記内側環体の外向きフランジの外周部を、上記二つの外側環体の少なくとも一方の外側環体の内周面に摺接させて、上記ラビリンスの形成された密封空間中に接触密封部を形成し、この接触密封部における上記内側環体および外側環体の少なくとも一方の周面側が潤滑性非金属素材からなることを特徴とする。
なお、好適には、上記外側環体の内周面に摺接する内側環体を、例えばポリテトラフルオロエチレン（ＰＴＦＥ）素材、硬質フェノール樹脂等の潤滑性非金属性素材自体で形成するのがよい。また、上記接触密封部における内側環体および外側環体の少なくとも一方の周面側を、上記潤滑性非金属性素材でコーティングしてもよい。
【０００７】
また、本発明に係る圧延機における密封形ころ軸受において、上記二つの隣接する外側環体の各フランジ間の内周面を軸線と平行な平行面に形成するとともに、上記外側環体と摺接する内側環体の外向きフランジの外周部を軸線と平行な折曲部に形成し、この折曲部を上記外側環体の平行面に摺接させたことを特徴とする。
【０００８】
また、本発明に係る圧延機における密封形ころ軸受において、上記二つの隣接する外側環体の各合わせ面内周部に対向する周状凹段部を形成するとともに、一方の外側環体の周状凹段部を傾斜面に形成し、上記外側環体と摺接する内側環体の外向きフランジの外周部を上記傾斜面に添わせて摺接させたことを特徴とする。
【０００９】
【発明の実施の形態】
以下、この発明の具体的実施例について図面を参照して説明する。
図１および図２は、この発明にかかる一実施例である。圧延機における密封形ころ軸受として、圧延機のロールネック（図示せず）を軸箱（図示せず）内に支承する４列円すいころ軸受１が記載されている。軸受１の左右両端部において、内輪２の小鍔側端部に外輪３の端面よりも軸方向に延長する延長環体部２ａが形成されている。２２は内・外輪２，３間に介装された円すいころである。
【００１０】
一方、外向きフランジ４ａ，５ａ，６ａをそれぞれ有する複数（この実施例では３個）の内側環体４，５，６が軸方向へ重合して連結された状態で、上記内輪２の延長環体部２ａの外周面に外嵌されている。また、外輪３の端面側には、内向きフランジ７ａ，８ａをそれぞれ有する複数（この実施例では２個）の金属製の外側環体７，８が、内側環体４，５，６と同心状に軸方向へ重合して連結された状態で位置させられている。上記３個の外向きフランジ４ａ，５ａ，６ａと２個の内向きフランジ７ａ，８ａは、軸方向両端部に外向きフランジ４ａ，５ａが位置するよう交互に並列して配置され、これらフランジ間の隙間によりラビリンス９が形成されている。すなわち、内側環体４，５，６および外側環体７，８は、軸受１の内側から外側へ向けて並ぶ各フランジの並列順序が外向きフランジ４ａから始まり外向きフランジ６ａで終わるように配列されている。これは、軸受回転時、遠心力で水等が外向きフランジ６ａにて振り飛ばされることを狙ったものである。
【００１１】
さらに、上記３個の内側環体４，５，６のうち、最も軸受内部に近い内側環体４が内輪２の延長環体部２ａに焼嵌めにて固着され、他の内側環体５，６は軸受分解時に分離可能なようにねじ１１にて上記焼嵌めされた内側環体４と締結固定されて内輪２の延長環体部２ａに緩く嵌合されている。さらに２個の外側環体７，８は軸受分解時に分離可能なようにねじ１２にて締結され、軸受内部側の外側環体７と外輪３とは外輪３の端面と着脱自在にインロウ結合１４されている。なお、Ｏリング１３が、外側環体７の外周部に形成した周溝１５に嵌合されて、軸箱の内周面と外側環体７の外周面を密封する。
【００１２】
また、上記３個の内側環体４，５，６のうち、軸方向両端部に位置する２個の内側環体４，６は金属製で断面Ｌ形にて形成され、強度維持と嵌合時の安定性を確実なものとしている。そして、上記Ｌ形の内側環体４，６の円筒部４ｂ，６ｂが対向して内輪２の延長環体部２ａに嵌合され、その円筒部４ｂ，６ｂ間に円板状の内側環体５が挾持されている。
【００１３】
上記円板状の内側環体５は、ポリテトラフルオロエチレン（ＰＴＦＥ）素材、硬質フェノール樹脂等の潤滑性非金属素材自体で形成されており、その外周部が外側環体８の内周面に軽く摺接させられている。これにより、上記非接触密封装置１０内部に接触密封部１６を形成している。なお、この内側環体５を金属製にて形成しその表面を上記潤滑性非金属素材でコーティングしてもよく、さらにはこの内輪環体５が摺接する外側環体８の内周面を上記潤滑性非金属素材でコーティングしてもよい。
【００１４】
上記円板状の内側環体５と外側環体７，８との摺接状態は次の通りである。すなわち、二つの隣接する外側環体７，８の各フランジ７ａ，８ａ間の内周面７ｂ，８ｂがそれぞれ軸受軸線と平行でかつ同一径の平行面に形成され、上記外側環体７と摺接する内側環体５の外向きフランジ５ａの外周部も軸受軸線と平行な折曲部１７に形成され、この折曲部１７が上記一方の外側環体８の平行面に摺接させられている。なお内側環体５の折曲部１７を両外側環体７，８の平行面にまたがって摺接させてもよい。この実施例の場合、内側環体５と外側環体８との摺接面が軸受軸線と平行とされているので、軸方向のガタがあっても摺接部の軽いしめしろの変化はなく一定に保たれる。
【００１５】
図３は上記円板状の内側環体５と外側環体７，８との摺接状態の別の実施例である。すなわち、上記二つの隣接する外側環体７，８の各合わせ面１８，１９内周部に、対向する周状凹段部２０，２１がそれぞれ形成されるとともに、他方の外側環体７の周状凹段部２０が軸線に対して９０度に近い角度を有する傾斜面に形成され、上記外側環体７と摺接する内側環体５の外向きフランジ５ａの外周部が上記傾斜面２０に添わせて軽く摺接させられている。この円板状の内側環体５と軸受外方側の断面Ｌ形内側環体６の円筒部６ａ間には、円板状のバッキング部材２２が介装されている。なお上記傾斜面２０の角度は上述のものに限定されるものではない。この実施例によれば、円板状の内側環体５の外周部を傾斜面２０に添わせるだけでよいため、内側環体５の外周部に成形加工不要であり、コスト低減につながる。さらに、バッキング部材２２により、内側環体５の外周部の外側環体７の傾斜面２０に対する摺接力の調整が容易である。
【００１６】
【発明の効果】
本発明では、軸受のラビリンスの形成された密封空間中に接触密封部を形成したので、圧延機の運転停止時や低速回転時に軸受内部へ水等の侵入を防止することができる。
【図面の簡単な説明】
【図１】本発明の第一実施例の断面図である。
【図２】図１の密封装置の断面図である。
【図３】本発明の第二実施例の密封装置の断面図である。
【図４】従来軸受の断面図である。
【図５】図４の密封装置の断面図である。
【符号の説明】
１ 軸受
２ 内輪
３ 外輪
４，５，６ 内側環体
４ａ，５ａ，６ａ 外向きフランジ
７，８ 外側環体
７ａ，８ａ 内向きフランジ
９ ラビリンス
１０ 非接触密封装置
１６ 接触密封部[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a sealed roller bearing in a rolling mill.
[0002]
[Prior art]
Conventionally, as a sealed roller bearing in a rolling mill, Japanese Patent Publication No. 3-66963 shown in FIGS. 4 and 5 is known. The conventional bearing 40 is a four-row tapered roller bearing that supports a roll neck 41 of a rolling mill in a shaft box 54. At both ends of the bearing 40, an extended ring portion 42a extending in the axial direction from the end surface of the outer ring 43 is formed on the small ring side of the inner ring 42, and outward flanges 44a, 45a, 46a are formed on the extended ring portion 42a. The three inner ring bodies 44, 45, and 46 each having the above are externally fitted in a state where they are overlapped and connected in the axial direction. Further, two outer ring bodies 47 and 48 having inward flanges 47a and 48a, respectively, are concentrically connected to the inner ring bodies 44, 45, and 46 in the axial direction and connected to the end face side of the outer ring 43. Is positioned in a state. The plurality of outward flanges 44a, 45a, 46a and the plurality of inward flanges 47a, 48a are arranged so that the outward flanges 44a, 44c are located at both ends in the axial direction and are alternately arranged in parallel. In this way, the labyrinth 49 is formed between the outer periphery of the inner ring bodies 44, 45, 46 and the inner periphery of the outer ring bodies 47, 48, and the non-contact sealing device 50 is configured.
[0003]
Of the three inner ring bodies 44, 45, 46, the inner ring body 44 closest to the inside of the bearing is fixed to the extended ring body portion 42 a of the inner ring 22 by shrink fitting, and the other inner ring bodies 45, 46 is fastened and fixed to the inner ring body 44 by a screw 51 so as to be separable. Further, the two outer ring bodies 47 and 48 are fastened by screws 52 so as to be separable, and the outer ring body 47 and the outer ring 43 on the bearing inner side are detachably in-row connected to the end face of the outer ring 43. Reference numeral 53 denotes an O-ring which is fitted in a circumferential groove 55 formed on the outer peripheral portion of the outer ring body 47 and seals the inner peripheral surface of the axle box 54 and the outer peripheral surface of the outer ring body 47. Reference numeral 55 denotes a tapered roller interposed between the inner and outer rings.
[0004]
[Problems to be solved by the invention]
However, in the above-described bearing 40, when the rolling mill rotates at high speed, a strong air curtain is created in the non-contact sealing device 50, and intrusion of cooling water and dust used in the rolling mill into the bearing 40 is prevented. High sealing performance can be obtained. However, because of the labyrinth configuration, there is a risk that water or the like accumulated in the non-contact sealing device 50 when the rolling mill is stopped travels through the labyrinth and enters the bearing 40 when the operation starts. Furthermore, even when the rolling mill is operated at a low speed according to the rolling schedule, the air curtain of the non-contact sealing device 50 is weak, so that water or the like may enter the bearing 40.
[0005]
Accordingly, an object of the present invention is to provide a sealed roller bearing in a rolling mill that prevents water and the like from entering the bearing when the rolling mill is stopped or rotated at a low speed.
[0006]
[Means for Solving the Problems]
As a means for solving the above problems, the inner ring edge portion, arranged by polymerizing in the axial direction a plurality of inner annular body having an outward flange, the end portion of the outer ring, a plurality of outer having an inward flange The ring is superposed in the axial direction and arranged concentrically with the inner ring, and the outward flange and the inward flange are alternately arranged so that the outward flanges are positioned at both axial ends. by the bearing seal type roller in the rolling machine to form a sealed space that is a labyrinth, the outer peripheral portion of the outward flange of the inner ring member positioned between the inward flanges of two adjacent said outer ring member, the two- one of by sliding contact with the inner peripheral surface of at least one of the outer ring of the outer ring member, form a contact seal in a sealed space formed in the labyrinth, the inner ring member and the outer ring in the contact seal body At least one peripheral surface side is characterized by comprising a lubricating non-metallic material.
Preferably, the inner ring that is in sliding contact with the inner peripheral surface of the outer ring is formed of a lubricious non-metallic material such as a polytetrafluoroethylene (PTFE) material or a hard phenol resin. . In addition, at least one peripheral surface side of the inner ring body and the outer ring body in the contact seal portion may be coated with the lubricating non-metallic material.
[0007]
Further, in the sealed roller bearing in the rolling mill according to the present invention, the inner peripheral surface between the flanges of the two adjacent outer ring bodies is formed in a parallel plane parallel to the axis, and is in sliding contact with the outer ring body. The outer peripheral part of the outward flange of the inner ring is formed in a bent part parallel to the axis, and this bent part is slidably contacted with the parallel surface of the outer ring.
[0008]
Further, in the sealed roller bearing in the rolling mill according to the present invention, a circumferential concave step portion is formed opposite to each of the mating surface inner peripheral portions of the two adjacent outer ring bodies, and the circumference of one outer ring body is formed. A concave concave portion is formed on the inclined surface, and the outer peripheral portion of the outward flange of the inner ring body that is in sliding contact with the outer ring body is brought into sliding contact with the inclined surface.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Specific embodiments of the present invention will be described below with reference to the drawings.
1 and 2 show an embodiment according to the present invention. As a sealed roller bearing in a rolling mill, a four-row tapered roller bearing 1 that supports a roll neck (not shown) of a rolling mill in a shaft box (not shown) is described. At both the left and right ends of the bearing 1, extended ring bodies 2 a that extend in the axial direction from the end face of the outer ring 3 are formed at the edge of the inner ring 2 on the small collar side. A tapered roller 22 is interposed between the inner and outer rings 2 and 3.
[0010]
On the other hand, in a state where a plurality (three in this embodiment) of inner ring bodies 4, 5, 6 each having outward flanges 4a, 5a, 6a are connected in an axially overlapping manner, It is fitted on the outer peripheral surface of the body part 2a. Further, a plurality of (two in this embodiment) metal outer ring bodies 7 and 8 each having inward flanges 7 a and 8 a are concentric with the inner ring bodies 4, 5 and 6 on the end face side of the outer ring 3. It is positioned in a state where it is overlapped and connected in the axial direction. The three outward flanges 4a, 5a, 6a and the two inward flanges 7a, 8a are alternately arranged in parallel so that the outward flanges 4a, 5a are positioned at both ends in the axial direction. A labyrinth 9 is formed by the gap. That is, the inner ring bodies 4, 5, 6 and the outer ring bodies 7, 8 are arranged so that the parallel order of the flanges arranged from the inside to the outside of the bearing 1 starts from the outward flange 4 a and ends at the outward flange 6 a. Has been. This is intended to cause water or the like to be shaken off by the outward flange 6a by centrifugal force when the bearing rotates.
[0011]
Further, of the three inner ring bodies 4, 5 and 6, the inner ring body 4 closest to the inside of the bearing is fixed to the extended ring body portion 2a of the inner ring 2 by shrink fitting, and the other inner ring bodies 5 and 5 are fixed. 6 is fastened and fixed to the inner ring body 4 that has been shrink-fitted with a screw 11 so as to be separable when the bearing is disassembled, and is loosely fitted to the extended ring body portion 2 a of the inner ring 2. Further, the two outer ring bodies 7 and 8 are fastened by screws 12 so as to be separable when the bearing is disassembled, and the outer ring body 7 and the outer ring 3 on the bearing inner side are detachably connected to the end face of the outer ring 3 by an in-row coupling 14. Has been. The O-ring 13 is fitted in a circumferential groove 15 formed in the outer peripheral portion of the outer ring body 7 to seal the inner peripheral surface of the axle box and the outer peripheral surface of the outer ring body 7.
[0012]
Of the three inner ring bodies 4, 5 and 6, the two inner ring bodies 4 and 6 located at both end portions in the axial direction are made of metal and have an L-shaped cross section, and maintain strength and fit. The stability of time is ensured. The cylindrical portions 4b and 6b of the L-shaped inner ring bodies 4 and 6 face each other and are fitted to the extended ring body portion 2a of the inner ring 2, and a disk-shaped inner ring body is interposed between the cylindrical portions 4b and 6b. 5 is held.
[0013]
The disk-shaped inner ring body 5 is formed of a lubricious non-metallic material itself such as a polytetrafluoroethylene (PTFE) material or a hard phenol resin, and its outer peripheral portion is on the inner peripheral surface of the outer ring body 8. It is lightly touched. Thereby, the contact sealing part 16 is formed inside the non-contact sealing device 10. The inner ring body 5 may be made of metal, and the surface thereof may be coated with the lubricating non-metallic material. Further, the inner peripheral surface of the outer ring body 8 with which the inner ring ring body 5 is slidably in contact is formed. It may be coated with a lubricious non-metallic material.
[0014]
The sliding contact state between the disk-shaped inner ring body 5 and the outer ring bodies 7 and 8 is as follows. That is, the inner peripheral surfaces 7b and 8b between the flanges 7a and 8a of two adjacent outer ring bodies 7 and 8 are formed in parallel planes parallel to the bearing axis and having the same diameter. The outer peripheral portion of the outward flange 5a of the inner ring body 5 in contact is also formed in a bent portion 17 parallel to the bearing axis, and the bent portion 17 is slidably contacted with the parallel surface of the one outer ring body 8. . The bent portion 17 of the inner ring body 5 may be slidably brought into contact with the parallel surfaces of the outer ring bodies 7 and 8. In the case of this embodiment, since the sliding contact surface between the inner ring body 5 and the outer ring body 8 is parallel to the bearing axis, there is no change in the light interference of the sliding contact portion even if there is axial backlash. Kept constant.
[0015]
FIG. 3 shows another embodiment of the sliding contact state between the disc-shaped inner ring body 5 and the outer ring bodies 7 and 8. That is, opposing circumferential concave steps 20 and 21 are respectively formed on the inner peripheral portions of the mating surfaces 18 and 19 of the two adjacent outer ring bodies 7 and 8, and the circumference of the other outer ring body 7 is formed. The concave stepped portion 20 is formed on an inclined surface having an angle close to 90 degrees with respect to the axis, and the outer peripheral portion of the outward flange 5a of the inner ring body 5 that is in sliding contact with the outer ring body 7 is attached to the inclined surface 20. It is touched lightly. A disk-shaped backing member 22 is interposed between the disk-shaped inner ring body 5 and the cylindrical portion 6a of the L-shaped inner ring body 6 on the outer side of the bearing. The angle of the inclined surface 20 is not limited to that described above. According to this embodiment, since the outer peripheral portion of the disk-shaped inner ring body 5 only needs to be attached to the inclined surface 20, the outer peripheral portion of the inner ring body 5 is not required to be molded, leading to cost reduction. Furthermore, the backing member 22 makes it easy to adjust the sliding contact force of the outer peripheral portion of the inner ring body 5 with the inclined surface 20 of the outer ring body 7.
[0016]
【The invention's effect】
In the present invention, since the contact sealing portion is formed in the sealed space where the labyrinth of the bearing is formed, it is possible to prevent water or the like from entering the bearing when the rolling mill is stopped or rotated at a low speed.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a first embodiment of the present invention.
FIG. 2 is a cross-sectional view of the sealing device of FIG.
FIG. 3 is a cross-sectional view of a sealing device according to a second embodiment of the present invention.
FIG. 4 is a cross-sectional view of a conventional bearing.
5 is a cross-sectional view of the sealing device of FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Bearing 2 Inner ring 3 Outer ring 4, 5, 6 Inner ring body 4a, 5a, 6a Outward flange 7, 8 Outer ring body 7a, 8a Inward flange 9 Labyrinth 10 Non-contact sealing device 16 Contact sealing part

Claims (3)

内輪の端部に、外向きフランジを有する複数の内側環体を軸方向に重合して配列し、外輪の端部に、内向きフランジを有する複数の外側環体を軸方向に重合しかつ内側環体と同心状に配列し、外向きフランジが軸方向両端部に位置するよう外向きフランジと内向きフランジとを交互に配列してこれらフランジ間の隙間によりラビリンスとされた密封空間を形成した圧延機における密封形ころ軸受において、二つの隣接する上記外側環体の内向きフランジ間に位置する上記内側環体の外向きフランジの外周部を、上記二つの外側環体の少なくとも一方の外側環体の内周面に摺接させて、上記ラビリンスの形成された密封空間中に接触密封部を形成し、この接触密封部における上記内側環体および外側環体の少なくとも一方の周面側が潤滑性非金属素材からなることを特徴とする圧延機における密封形ころ軸受。A plurality of inner ring bodies having outward flanges are arranged in an axial direction at the end of the inner ring, and a plurality of outer ring bodies having inward flanges are overlapped in the axial direction at the end of the outer ring. Arranged concentrically with the ring body, the outward flange and the inward flange are alternately arranged so that the outward flanges are located at both ends in the axial direction, thereby forming a labyrinth sealed space between the flanges. in the bearing sealing type roller in the rolling mill, at least one outer ring of two adjacent an outer periphery of the outward flange of the inner ring member positioned between the inward flange of the outer ring member, the two outer annular body A contact sealing portion is formed in the sealed space where the labyrinth is formed by sliding contact with the inner peripheral surface of the body, and at least one peripheral surface side of the inner ring body and the outer ring body in the contact sealing portion is lubricated Non-gold Sealed type roller bearings in rolling mills characterized by comprising the material. 上記二つの隣接する外側環体の各フランジ間の内周面を軸線と平行な平行面に形成するとともに、上記外側環体と摺接する内側環体の外向きフランジの外周部を軸線と平行な折曲部に形成し、この折曲部を上記外側環体の平行面に摺接させたことを特徴とする請求項１に記載の圧延機における密封形ころ軸受。  The inner peripheral surface between the flanges of the two adjacent outer ring bodies is formed in a parallel plane parallel to the axis line, and the outer peripheral part of the outward flange of the inner ring body that is in sliding contact with the outer ring body is parallel to the axis line. The hermetic roller bearing for a rolling mill according to claim 1, characterized in that it is formed in a bent portion, and the bent portion is brought into sliding contact with the parallel surface of the outer ring body. 上記二つの隣接する外側環体の各合わせ面内周部に対向する周状凹段部を形成するとともに、一方の外側環体の周状凹段部を傾斜面に形成し、上記外側環体と摺接する内側環体の外向きフランジの外周部を上記傾斜面に添わせて摺接させたことを特徴とする請求項１に記載の圧延機における密封形ころ軸受。  Forming a circumferential concave step portion facing the inner peripheral portion of each mating surface of the two adjacent outer ring bodies, and forming a circumferential concave step portion of one outer ring body on the inclined surface; The sealed roller bearing for a rolling mill according to claim 1, wherein the outer peripheral portion of the outward flange of the inner ring body that is in sliding contact with the outer ring is in sliding contact with the inclined surface.
JP26027196A 1996-09-09 1996-09-09 Sealed roller bearings in rolling mills. Expired - Fee Related JP3646951B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP26027196A JP3646951B2 (en) 1996-09-09 1996-09-09 Sealed roller bearings in rolling mills.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP26027196A JP3646951B2 (en) 1996-09-09 1996-09-09 Sealed roller bearings in rolling mills.

Publications (2)

Publication Number Publication Date
JPH1085809A JPH1085809A (en) 1998-04-07
JP3646951B2 true JP3646951B2 (en) 2005-05-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3748182A1 (en) * 2019-06-04 2020-12-09 IMO Holding GmbH Roller bearing arrangement with a sealing device for sealing the bearing gap

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3988397B2 (en) * 2001-02-27 2007-10-10 オイレス工業株式会社 Synthetic plastic plain bearing
CN108326080A (en) * 2018-04-20 2018-07-27 襄阳振本传动设备有限公司 A kind of aligning roller assembly

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3748182A1 (en) * 2019-06-04 2020-12-09 IMO Holding GmbH Roller bearing arrangement with a sealing device for sealing the bearing gap

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