JPH05149329A - Radial roller bearing - Google Patents
Radial roller bearingInfo
- Publication number
- JPH05149329A JPH05149329A JP3314785A JP31478591A JPH05149329A JP H05149329 A JPH05149329 A JP H05149329A JP 3314785 A JP3314785 A JP 3314785A JP 31478591 A JP31478591 A JP 31478591A JP H05149329 A JPH05149329 A JP H05149329A
- Authority
- JP
- Japan
- Prior art keywords
- rolling
- raceway
- raceway surface
- inner ring
- shaft
- 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.)
- Granted
Links
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
- 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
- F16C19/24—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 radial load mainly
- F16C19/26—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 radial load mainly with a single row of rollers
-
- 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、たとえば鋼板の溶融
金属めっき槽などに用いられるラジアルころ軸受に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a radial roller bearing used in, for example, a molten metal plating tank for steel sheets.
【０００２】[0002]
【従来の技術】鋼板の溶融金属めっき槽において、軸受
は、高温、高荷重状態で使用されるので、軸の軸方向の
熱膨張や、たわみなどの軸の熱変形による中心線の傾斜
を吸収する機能を備えていることが要求される。2. Description of the Related Art In a hot-dip galvanizing bath for steel sheets, bearings are used under high temperature and high load conditions, so that the axial expansion of the shaft and the inclination of the center line due to thermal deformation of the shaft such as bending are absorbed It is required to have the function to do.
【０００３】従来、溶融金属めっき槽で使用される軸受
として、軌道みぞを有するセラミックス製内輪と、内輪
の軌道みぞに配設される複数のセラミックス製玉と、こ
れらの玉との軸方向の相対的な移動が可能な円筒状また
は凹球面状軌道面を有するとともにハウジングにすきま
ばめされたセラミックス製外輪とからなるセラミックス
製総玉軸受が用いられている（実開昭６３−８９４２８
号参照）。Conventionally, as a bearing used in a molten metal plating bath, a ceramic inner ring having a raceway groove, a plurality of ceramic balls arranged in the raceway groove of the inner ring, and an axial relative relationship between these balls. A ceramic full ball bearing is used which has a cylindrical or concave spherical raceway surface that can be moved in a uniform manner, and a ceramic outer ring that is loosely fitted in a housing (Actual No. Sho 63-89428).
No.).
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、従来の
玉軸受では、外輪の軌道面と玉とが１点で接触するの
で、大きな荷重がかかると外輪軌道面と玉との間に大き
な接触応力が発生し、短期間の使用で摩耗して寿命が短
くなるという問題がある。However, in the conventional ball bearing, since the raceway surface of the outer ring and the ball contact at one point, a large load causes a large contact stress between the raceway surface of the outer ring and the ball. It is generated, and there is a problem that it wears out after a short period of use and shortens the life.
【０００５】この発明の目的は、上記問題を解決したラ
ジアルころ軸受を提供することにある。An object of the present invention is to provide a radial roller bearing that solves the above problems.
【０００６】[0006]
【課題を解決するための手段】この発明によるラジアル
ころ軸受は、内外両輪と、ころとよりなるラジアルころ
軸受であって、内輪の軌道面が内輪中心を中心とする凸
球面となされ、外輪の軌道面が外輪中心を中心とする円
筒面となされ、ころの周面の長さの中間部に、内輪の軌
道面と同一曲率もしくはこれよりも小さい曲率を有する
凹球面状となされた内輪に対する第１転動面が形成さ
れ、第１転動面の両側に、それぞれ円筒面状となされた
外輪に対する第２転動面が形成されているものである。A radial roller bearing according to the present invention is a radial roller bearing composed of inner and outer wheels and rollers, wherein the raceway surface of the inner ring is a convex spherical surface centered on the center of the inner ring. The raceway surface is a cylindrical surface centered on the center of the outer ring, and in the middle part of the length of the circumferential surface of the roller, the first ring for the inner ring with the same spherical curvature as the raceway surface of the inner ring or a curvature smaller than that One rolling surface is formed, and on both sides of the first rolling surface, the second rolling surface for the outer ring, which has a cylindrical surface shape, is formed.
【０００７】[0007]
【作用】内輪の軌道面が内輪中心を中心とする凸球面と
なされ、ころの周面の長さの中間部に、内輪の軌道面と
同一曲率もしくはこれよりも小さい曲率を有する凹球面
状となされた内輪に対する第１転動面が形成されている
ので、軸にたわみのような熱変形が生じて中心線が傾斜
した場合、内輪の軌道面がころの第１転動面に対して摺
動し、内輪がころおよび外輪に対して傾動することによ
り上記軸の中心線の傾斜が吸収される。また、外輪の軌
道面が外輪中心を中心とする円筒面となされ、ころの周
面における第１転動面の両側に、それぞれ円筒面状とな
された外輪に対する第２転動面が形成されているので、
軸が熱膨張によりスラスト方向に伸びた場合、ころの２
つの第２転動面が、外輪の軌道面に沿って摺動し、内輪
およびころが外輪に対して移動することにより上記軸の
伸びが吸収される。[Operation] The raceway surface of the inner ring is a convex spherical surface centered on the center of the inner ring, and a concave spherical surface having the same curvature as or less than that of the raceway surface of the inner ring is formed in the middle portion of the length of the peripheral surface of the roller. Since the first rolling surface for the inner ring is formed, the raceway surface of the inner ring slides against the first rolling surface of the roller when the center line is inclined due to thermal deformation such as bending of the shaft. When the inner ring moves, the inner ring tilts with respect to the rollers and the outer ring, whereby the inclination of the center line of the shaft is absorbed. In addition, the raceway surface of the outer ring is formed as a cylindrical surface centered on the center of the outer ring, and the second rolling surface for the outer ring, which is formed into a cylindrical surface shape, is formed on both sides of the first rolling surface on the circumferential surface of the roller. Because
If the shaft expands in the thrust direction due to thermal expansion,
The two second rolling surfaces slide along the raceway surface of the outer ring, and the inner ring and the rollers move with respect to the outer ring, whereby the elongation of the shaft is absorbed.
【０００８】[0008]
【実施例】以下、この発明の１実施例を、図面を参照し
て説明する。この実施例は、この発明による軸受を、保
持器のない総ころ軸受に適用したものである。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. In this embodiment, the bearing according to the present invention is applied to a full complement roller bearing having no cage.
【０００９】ラジアルころ軸受は、内外両輪(1)(2)と、
ころ(3)とよりなる。内外両輪(1)(2)は、それぞれ窒化
ケイ素などのセラミックス、耐食耐熱鋼などで形成され
る。耐食耐熱鋼で形成される場合、その表面に、主に耐
食性向上を目的としたコーティングを施しておくのがよ
い。このコーティングは、たとえばアルミナ、酸化クロ
ム、窒化チタン、炭化チタンなどのセラミックスを用い
て施される。ころ(3)は、窒化ケイ素などのセラミック
スで形成される。The radial roller bearing is composed of inner and outer wheels (1) and (2),
Composed of Koro (3). Both the inner and outer wheels (1) and (2) are made of ceramics such as silicon nitride or corrosion resistant heat resistant steel. When it is made of corrosion resistant heat resistant steel, it is preferable to coat the surface thereof mainly for the purpose of improving corrosion resistance. This coating is applied using ceramics such as alumina, chromium oxide, titanium nitride, and titanium carbide. The roller (3) is made of ceramics such as silicon nitride.
【００１０】内輪(1) の軌道面(1a)は、内輪(1) 中心、
すなわち内輪(1) の中心線と、長さ方向の中心を含む垂
直面との交点を中心とする凸球面状となされている。外
輪(2) の軌道面(2a)は、外輪(2) 中心を中心とする円筒
面状となされている。ころ(3) の周面の長さの中間部
に、内輪(1) の軌道面(1a)と同一曲率の凹球面状となさ
れた内輪(1) に対する第１転動面(3a)が形成されてい
る。第１転動面(3a)は、内輪(1) の軌道面(1a)の中心を
中心としかつこれと同一曲率の円弧を、ころ(3) の中心
線の周囲に回転させたときに生じる凹球面である。ま
た、第１転動面(3a)の両側に、それぞれ円筒面状となさ
れた外輪(2) に対する第２転動面(3b)が形成されてい
る。The raceway (1a) of the inner ring (1) is the center of the inner ring (1),
That is, the inner ring (1) has a convex spherical shape centered on the intersection of the centerline and the vertical plane including the center in the longitudinal direction. The raceway surface (2a) of the outer ring (2) has a cylindrical surface shape centered on the center of the outer ring (2). The first rolling surface (3a) for the inner ring (1), which has a concave spherical shape with the same curvature as the raceway surface (1a) of the inner ring (1), is formed in the middle of the length of the peripheral surface of the roller (3). Has been done. The first rolling surface (3a) occurs when an arc centered on the center of the raceway (1a) of the inner ring (1) and having the same curvature as this is rotated around the center line of the roller (3). It is a concave spherical surface. Further, on both sides of the first rolling surface (3a), there are formed second rolling surfaces (3b) for the outer ring (2) which are cylindrical.
【００１１】このような構成において、図示しない軸に
たわみのような熱変形が生じて中心線が傾斜した場合、
内輪(1) の軌道面(1a)がころ(3) の第１転動面(3a)に対
して摺動し、内輪(1) がころ(3) および外輪(2) に対し
て傾動することにより上記軸の中心線の傾斜が吸収され
る。また、軸が熱膨張によりスラスト方向に伸びた場
合、ころ(3) の２つの第２転動面(3b)が、外輪(2) の軌
道面(2a)に沿って摺動し、内輪(1) およびころ(3) が外
輪(2) に対して移動することにより上記軸の伸びが吸収
される。In such a structure, when a shaft (not shown) undergoes thermal deformation such as bending and the center line is inclined,
The raceway (1a) of the inner ring (1) slides against the first rolling surface (3a) of the roller (3), and the inner ring (1) tilts with respect to the roller (3) and the outer ring (2). As a result, the inclination of the center line of the axis is absorbed. When the shaft expands in the thrust direction due to thermal expansion, the two second rolling surfaces (3b) of the rollers (3) slide along the raceway surface (2a) of the outer ring (2), and the inner ring ( The movement of 1) and the roller (3) with respect to the outer ring (2) absorbs the elongation of the shaft.
【００１２】上記実施例においては、ころ(3) の第１転
動面(3a)は、内輪(1) の軌道面(1a)と同一曲率の凹球面
状となされているが、これに限るものではなく、たとえ
ば第１転動面(3a)は軌道面(1a)よりも小さい曲率の凹球
面状となされていてもよい。In the above embodiment, the first rolling surface (3a) of the roller (3) is a concave spherical surface having the same curvature as the raceway surface (1a) of the inner ring (1), but this is not the only option. For example, the first rolling surface (3a) may be a concave spherical surface having a curvature smaller than that of the raceway surface (1a).
【００１３】[0013]
【発明の効果】この発明のラジアルころ軸受によれば、
上述のように、軸の中心線の傾斜およびスラスト方向の
伸びが吸収される。しかも、軸の中心線の傾斜の吸収
は、内輪の凸球面状軌道面がころの凹球面状第１転動面
に対して摺動することにより行われ、軸のスラスト方向
の伸びの吸収は、ころの２つの円筒面状第２転動面が、
外輪の円筒面状軌道面に沿って摺動することにより行わ
れるので、いずれの場合にも面接触することになり、発
生する接触応力は、従来の軸受よりも小さくなる。した
がって、内外両輪およびころに摩耗が生じ難くなって寿
命が向上する。According to the radial roller bearing of the present invention,
As described above, the inclination of the center line of the shaft and the elongation in the thrust direction are absorbed. Moreover, the absorption of the inclination of the center line of the shaft is performed by the convex spherical raceway surface of the inner ring sliding on the concave spherical first rolling surface of the roller, and the absorption of the expansion of the shaft in the thrust direction is absorbed. , The two second cylindrical rolling surfaces of the rollers are
Since it is performed by sliding along the cylindrical raceway surface of the outer ring, surface contact occurs in any case, and the generated contact stress is smaller than that of the conventional bearing. Therefore, the inner and outer wheels and the rollers are less likely to be worn, and the life is improved.
【図１】この発明によるラジアルころ軸受の縦断面図で
ある。FIG. 1 is a vertical sectional view of a radial roller bearing according to the present invention.
１ 内輪 １ａ 軌道面 ２ 外輪 ２ａ 軌道面 ３ ころ ３ａ 第１転動面 ３ｂ 第２転動面 1 Inner ring 1a Raceway surface 2 Outer ring 2a Raceway surface 3 Roller 3a 1st rolling surface 3b 2nd rolling surface
───────────────────────────────────────────────────── フロントページの続き (72)発明者 矢野 広 大阪市中央区南船場三丁目５番８号 光洋 精工株式会社内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiroshi Yano 3-5-8 Minamisenba, Chuo-ku, Osaka City Koyo Seiko Co., Ltd.
Claims (1)
ろ軸受であって、内輪の軌道面が内輪中心を中心とする
凸球面となされ、外輪の軌道面が外輪中心を中心とする
円筒面となされ、ころの周面の長さの中間部に、内輪の
軌道面と同一曲率もしくはこれよりも小さい曲率を有す
る凹球面状となされた内輪に対する第１転動面が形成さ
れ、第１転動面の両側に、それぞれ円筒面状となされた
外輪に対する第２転動面が形成されているラジアルころ
軸受。1. A radial roller bearing comprising inner and outer wheels and rollers, wherein the raceway surface of the inner ring is a convex spherical surface centered on the center of the inner ring, and the raceway surface of the outer ring is a cylindrical surface centered on the center of the outer ring. The first rolling surface for the inner ring, which has a concave spherical shape and has the same curvature as or smaller than that of the raceway surface of the inner ring, is formed in the middle of the length of the circumferential surface of the roller. A radial roller bearing having, on both sides of the surface, second rolling surfaces for the outer ring, each of which has a cylindrical shape.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3314785A JP2997825B2 (en) | 1991-11-28 | 1991-11-28 | Radial roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3314785A JP2997825B2 (en) | 1991-11-28 | 1991-11-28 | Radial roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05149329A true JPH05149329A (en) | 1993-06-15 |
| JP2997825B2 JP2997825B2 (en) | 2000-01-11 |
Family
ID=18057568
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3314785A Expired - Fee Related JP2997825B2 (en) | 1991-11-28 | 1991-11-28 | Radial roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2997825B2 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6709164B2 (en) | 2001-04-12 | 2004-03-23 | Nsk Ltd. | Tapered roller bearing |
| KR100711444B1 (en) * | 2005-12-23 | 2007-04-24 | 주식회사 포스코 | Bearing device for zinc pot roll in continuous galvanizing line |
| US7255483B1 (en) * | 2001-03-03 | 2007-08-14 | United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Thrust rollers |
| JP2011085137A (en) * | 2009-10-13 | 2011-04-28 | Mahle Internatl Gmbh | Internal combustion engine having at least one camshaft |
| JP2016196883A (en) * | 2015-04-06 | 2016-11-24 | ゼネラル・エレクトリック・カンパニイ | Fan bearings for turbine engine |
| US9869190B2 (en) | 2014-05-30 | 2018-01-16 | General Electric Company | Variable-pitch rotor with remote counterweights |
| US10072510B2 (en) | 2014-11-21 | 2018-09-11 | General Electric Company | Variable pitch fan for gas turbine engine and method of assembling the same |
| US10100653B2 (en) | 2015-10-08 | 2018-10-16 | General Electric Company | Variable pitch fan blade retention system |
| US11674435B2 (en) | 2021-06-29 | 2023-06-13 | General Electric Company | Levered counterweight feathering system |
| US11795964B2 (en) | 2021-07-16 | 2023-10-24 | General Electric Company | Levered counterweight feathering system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338156A (en) * | 2010-07-15 | 2012-02-01 | 邹先春 | Convex-track bearing capable of automatically discharging dust |
-
1991
- 1991-11-28 JP JP3314785A patent/JP2997825B2/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7255483B1 (en) * | 2001-03-03 | 2007-08-14 | United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Thrust rollers |
| US6709164B2 (en) | 2001-04-12 | 2004-03-23 | Nsk Ltd. | Tapered roller bearing |
| KR100711444B1 (en) * | 2005-12-23 | 2007-04-24 | 주식회사 포스코 | Bearing device for zinc pot roll in continuous galvanizing line |
| WO2007073060A1 (en) * | 2005-12-23 | 2007-06-28 | Posco | Bearing device for roll of hot dipping bath in continuous hot dip coating line |
| US8047718B2 (en) | 2005-12-23 | 2011-11-01 | Posco | Bearing device for roll of hot dipping bath in continuous hot dip coating line |
| JP2011085137A (en) * | 2009-10-13 | 2011-04-28 | Mahle Internatl Gmbh | Internal combustion engine having at least one camshaft |
| US9869190B2 (en) | 2014-05-30 | 2018-01-16 | General Electric Company | Variable-pitch rotor with remote counterweights |
| US10072510B2 (en) | 2014-11-21 | 2018-09-11 | General Electric Company | Variable pitch fan for gas turbine engine and method of assembling the same |
| JP2016196883A (en) * | 2015-04-06 | 2016-11-24 | ゼネラル・エレクトリック・カンパニイ | Fan bearings for turbine engine |
| US10100653B2 (en) | 2015-10-08 | 2018-10-16 | General Electric Company | Variable pitch fan blade retention system |
| US11674435B2 (en) | 2021-06-29 | 2023-06-13 | General Electric Company | Levered counterweight feathering system |
| US11795964B2 (en) | 2021-07-16 | 2023-10-24 | General Electric Company | Levered counterweight feathering system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2997825B2 (en) | 2000-01-11 |
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