JPS6298025A - Cylindrical roller bearing - Google Patents
Cylindrical roller bearingInfo
- Publication number
- JPS6298025A JPS6298025A JP60238271A JP23827185A JPS6298025A JP S6298025 A JPS6298025 A JP S6298025A JP 60238271 A JP60238271 A JP 60238271A JP 23827185 A JP23827185 A JP 23827185A JP S6298025 A JPS6298025 A JP S6298025A
- Authority
- JP
- Japan
- Prior art keywords
- ring raceway
- raceway surface
- cylindrical roller
- outer ring
- circumferential groove
- 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.)
- Pending
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
- 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
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the 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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
-
- 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、モーター等に使用される円筒ころ軸受に関す
る。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to cylindrical roller bearings used in motors and the like.
従来技術
中、大型モーターには、円筒ころ軸受と玉軸受との組合
せが一般的に採用されているか、この場合使用中に異常
音（金属的な音圧レベルの高い音で、運転条件により連
続的あるいは間歇的に発生し、一般的にきしり音と呼ば
れる）が生じ易く、その対策として軸受の組み付は後の
すきま（残留すきま）を小さくするとか、特公昭４４−
１５６８９号のように外輪軌道面に浅い円周調を設ける
等か知られている。Among conventional technologies, a combination of cylindrical roller bearings and ball bearings is generally adopted for large motors, or in this case, abnormal noises (metallic sound with high sound pressure level, continuous depending on operating conditions) may occur during use. To counter this, it is recommended to minimize the clearance (residual clearance) after assembling the bearing.
It is known to provide a shallow circumferential pitch on the outer ring raceway surface as in No. 15689.
従来技術の問題点
しかし、軸受の組み付は後のすきま（残留すきま）を小
さくするには、軸受すきまの範囲を小さく仕上げなけれ
ばならず、また軸と内輪のはめあいを選択組合せしなけ
ればならず、軸受の加工と組み付けに手間がかかり、費
用高となる。最近モーターが高速化してきているが、こ
の場合残留すきまが小さいと発熱が太き（温度上昇が高
くなり、ますますすきま選定が難しくなってきている。Problems with conventional technology However, in order to reduce the clearance (residual clearance) after assembling the bearing, the range of bearing clearance must be made small, and the fit between the shaft and inner ring must be selected and combined. First, the processing and assembly of the bearings is time consuming and costly. Recently, motors have become faster, but in this case, if the residual clearance is small, heat generation increases (temperature rise increases, making it increasingly difficult to select the clearance).
また特公昭４４−１５６８９号のように外輪軌道面に浅
い円周溝を設ける対策も十分な効果を奏することかでき
ないといわれている。Furthermore, it is said that the measure of providing a shallow circumferential groove on the outer ring raceway surface as disclosed in Japanese Patent Publication No. 44-15689 is not sufficiently effective.
円部ころ軸受は、ラジアル荷重下で使用されるか、この
場合潤滑剤の粘性と撹拌抵抗でころの自転、公転に遅れ
を生じ易く、自転、公転に遅れを生ずることは、転がり
面にすべりが発生していることを示し、このすべりと転
がり面の潤滑油膜状咀とのある関係下できしり音が発生
すると考えられている。このことは残留すきまを小さく
すると、すべりが小さくなり、きしり音が発生しにくく
なることでも分かる。Circular roller bearings are used under radial load, or in this case, the viscosity of the lubricant and stirring resistance tend to cause delays in the rotation and revolution of the rollers.Delays in rotation and revolution are caused by slippage on the rolling surface. It is thought that the squealing noise occurs due to a certain relationship between this slip and the lubricating oil film on the rolling surface. This can also be seen by the fact that when the residual clearance is made smaller, the slippage becomes smaller, making it difficult to generate squealing noise.
問題点を解決しようとする手段
本発明は、外輪軌道面に周溝を設け、該周溝内に前記外
輪軌道径より小さい内径を有しかつ径を拡張及び収縮可
能な弾性リングを遊嵌合して外輪軌道面と内輪軌道面間
に配列された円筒ころに半径方向内方への予圧を付′Ｊ
−した円筒ころ軸受とすることにより上記問題点を解決
するものである。Means for Solving the Problems The present invention provides a circumferential groove on the outer ring raceway surface, and loosely fits into the circumferential groove an elastic ring that has an inner diameter smaller than the outer ring raceway diameter and is capable of expanding and contracting the diameter. to apply a radially inward preload to the cylindrical rollers arranged between the outer ring raceway surface and the inner ring raceway surface.
The above-mentioned problems are solved by providing a cylindrical roller bearing with a cylindrical roller bearing.
作用
内輪軌道と外輪軌道間の円筒ころは、前記弾性リングに
より無負荷置でも常に半径方向内方への予圧を付与され
て内輪軌道に押し付けられる結果、駆動力を与えられて
自転、公転の遅れを少なくする。The cylindrical rollers between the inner ring raceway and the outer ring raceway are always radially inwardly preloaded by the elastic ring and pressed against the inner ring raceway even in a no-load state, and as a result, a driving force is applied to the cylindrical rollers, causing a delay in rotation and revolution. Reduce.
実施例
本発明の一実施例を図において説明する。第１図は本発
明の円筒ころ軸受の断面図であって、１は内周に軌道面
２を形成した外輪、３は外周に軌道面４を形成した内輪
、５は外輪軌道面２と内輪軌道面４との間に保持器６に
より円周略等間隔に配列された円筒ころである。そして
前記外輪軌道面２の略中夫には周溝７を設け、該周溝７
内に弾性リング８を遊嵌合して外輪軌道面２と内輪軌道
面４間に配列された円筒ころ５に半径方向内方への予圧
を付与して同ころ５を内輪軌道面４に押し付けている。Embodiment An embodiment of the present invention will be explained with reference to the drawings. FIG. 1 is a sectional view of a cylindrical roller bearing of the present invention, in which 1 is an outer ring with a raceway surface 2 formed on its inner periphery, 3 is an inner ring with a raceway surface 4 formed on its outer periphery, and 5 is an outer ring raceway surface 2 and an inner ring. These are cylindrical rollers that are arranged at approximately equal intervals around the circumference by a cage 6 between the rollers and the raceway surface 4. A circumferential groove 7 is provided approximately at the center of the outer ring raceway surface 2, and the circumferential groove 7
An elastic ring 8 is loosely fitted in the inner ring to apply a radially inward preload to the cylindrical rollers 5 arranged between the outer ring raceway surface 2 and the inner ring raceway surface 4 to press the rollers 5 against the inner ring raceway surface 4. ing.
目１１記弾性リング８は、前記外輪軌道面２の径りより
小さい内径ｄを有しかつ径を拡張及び収縮可能な鋼製リ
ングか好ましく、例えば第２図に示すように軸受と同軸
のコイルばねに形成すると、リングの切れ目による悪影
響がなく好ましい。しかし、軸受の組み立て時に前記弾
性リング８が径を拡張して円筒ころ５を内外軌道面２．
４間に配置させるため、軸受か組み立てられた時、前記
周溝７内においてリング外径と周溝７の底面間に適度の
半径方向すきまＳを形成させるようにしておくことか必
要である。さらに前記周溝７の両側面で弾性リング８を
軸方向に押さえると、弾性リング８の半径方向の弾性し
たがって円筒ころ５への予圧を減少するので、好ましく
ない。このため前記外輪軌道面２の周溝７は、深さ寸法
Ｈを前記弾性リング８の半径方向の厚み寸法Ｔより大き
く形成するとともに、幅寸法Ｗを弾性リング８の幅寸法
りより大きく形成しておくことが必要である。しかし前
記周溝７の両側面による弾性リング８の押さえ力か、リ
ング８の弾性の大きさに影響しない程度であれば、必ず
しも上記のような幅寸法ＷとＬに対する配慮は必要ない
。11. The elastic ring 8 is preferably a steel ring having an inner diameter d smaller than the diameter of the outer ring raceway surface 2 and capable of expanding and contracting in diameter. For example, as shown in FIG. 2, the elastic ring 8 is a steel ring coaxial with the bearing. Forming it into a spring is preferable since there is no adverse effect due to cuts in the ring. However, when assembling the bearing, the elastic ring 8 expands in diameter and the cylindrical roller 5 is attached to the inner and outer raceway surfaces 2.
4, it is necessary to form an appropriate radial gap S between the outer diameter of the ring and the bottom surface of the circumferential groove 7 in the circumferential groove 7 when the bearing is assembled. Furthermore, if the elastic ring 8 is pressed in the axial direction by both sides of the circumferential groove 7, the radial elasticity of the elastic ring 8 and, therefore, the preload on the cylindrical rollers 5 will be reduced, which is not preferable. Therefore, the circumferential groove 7 of the outer ring raceway surface 2 has a depth H larger than the radial thickness T of the elastic ring 8 and a width W larger than the width of the elastic ring 8. It is necessary to keep it. However, as long as the pressing force of the elastic ring 8 by both sides of the circumferential groove 7 does not affect the elasticity of the ring 8, the above-mentioned width dimensions W and L do not necessarily need to be considered.
第１表は本発明の円筒ころ軸受ＮＵ３１２を使用してき
しり音防止効果を確認したテスト結果を示す。このテス
ト結果から軸受の回転数か速いはと、符通品ではきしり
音が発生し易いが、本発明品ではきしり音は発生せず、
きしり音防止効果か認められた。Table 1 shows test results to confirm the squealing noise prevention effect using the cylindrical roller bearing NU312 of the present invention. This test result shows that when the rotation speed of the bearing is high, the standard product tends to produce squeaking noise, but the product of the present invention does not produce any squeaking noise.
It was recognized that it was effective in preventing squeak noise.
第１表
なお、前記弾性リング８は、図示のコイルばね状に限定
されず一箇所に切り目を有するリングでもよく、またそ
の断面形状は図示の矩形に限定されず、円形でもよい。Table 1 Note that the elastic ring 8 is not limited to the illustrated coil spring shape, but may be a ring having a cut at one location, and its cross-sectional shape is not limited to the illustrated rectangular shape, but may be circular.
効果
本発明は上記構成であるから、内輪軌道面２と外輪軌道
面４間の円筒ころ５が、前記弾性リング８により無負荷
置でも常に半径方向内方への予圧を付与されて内輪軌道
面２に押し付けられる結果、駆動力を与えられて自転と
公転の遅れが少なくなり、きしり音の発生を防止するこ
とができる。Effects Since the present invention has the above configuration, the cylindrical rollers 5 between the inner ring raceway surface 2 and the outer ring raceway surface 4 are always radially inwardly preloaded by the elastic ring 8 even under no load, so that the inner ring raceway surface As a result of being pressed against 2, a driving force is applied and the delay between rotation and revolution is reduced, making it possible to prevent the generation of squeaking noise.
第１図は本発明の一実施例の断面図、第２図は第１図の
弾性リングの軸受組み立て前の状態を示す断面図である
。FIG. 1 is a sectional view of an embodiment of the present invention, and FIG. 2 is a sectional view showing the elastic ring of FIG. 1 in a state before the bearing is assembled.
Claims (4)
道径より小さい内径を有しかつ径を拡張及び収縮可能な
弾性リングを遊嵌合して外輪軌道面と内輪軌道面間に配
列された円筒ころに半径方向内方への予圧を付与した円
筒ころ軸受(1) A circumferential groove is provided on the outer ring raceway surface, and an elastic ring having an inner diameter smaller than the outer ring raceway diameter and capable of expanding and contracting the diameter is loosely fitted into the circumferential groove to form an outer ring raceway surface and an inner ring raceway surface. Cylindrical roller bearing with radially inward preload applied to the cylindrical rollers arranged between them
向厚み寸法より大きい寸法の深さに形成されている特許
請求の範囲第１項記載の円筒ころ軸受(2) The cylindrical roller bearing according to claim 1, wherein the circumferential groove on the outer ring raceway surface is formed to a depth greater than the radial thickness dimension of the elastic ring.
されている特許請求の範囲第１項記載の円筒ころ軸受(3) The cylindrical roller bearing according to claim 1, wherein the circumferential groove of the outer ring raceway is formed at the center of the outer ring raceway.
る特許請求の範囲第１項ないし第３項記載の円筒ころ軸
受(4) The cylindrical roller bearing according to any one of claims 1 to 3, wherein the elastic ring is a coil spring coaxial with the bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60238271A JPS6298025A (en) | 1985-10-23 | 1985-10-23 | Cylindrical roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60238271A JPS6298025A (en) | 1985-10-23 | 1985-10-23 | Cylindrical roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6298025A true JPS6298025A (en) | 1987-05-07 |
Family
ID=17027701
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60238271A Pending JPS6298025A (en) | 1985-10-23 | 1985-10-23 | Cylindrical roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6298025A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6682226B2 (en) | 2002-05-09 | 2004-01-27 | The Timken Company | Cylindrical roller bearing with preload capability |
| WO2005075843A1 (en) * | 2004-02-03 | 2005-08-18 | Hansen Transmissions International, Naamloze Vennootschap | Roller bearing |
| US20130199320A1 (en) * | 2010-05-05 | 2013-08-08 | Robert Bosch Gmbh | Eccentric Bearing |
| CN105408645A (en) * | 2013-08-12 | 2016-03-16 | 舍弗勒技术股份两合公司 | Non-slip rolling bearing |
-
1985
- 1985-10-23 JP JP60238271A patent/JPS6298025A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6682226B2 (en) | 2002-05-09 | 2004-01-27 | The Timken Company | Cylindrical roller bearing with preload capability |
| WO2005075843A1 (en) * | 2004-02-03 | 2005-08-18 | Hansen Transmissions International, Naamloze Vennootschap | Roller bearing |
| CN100455833C (en) * | 2004-02-03 | 2009-01-28 | 汉森传动系统国际公司 | Roller bearing |
| US7537391B2 (en) | 2004-02-03 | 2009-05-26 | Hansen Transmissions International, Naamloze Vennootschap | Roller bearing |
| US20130199320A1 (en) * | 2010-05-05 | 2013-08-08 | Robert Bosch Gmbh | Eccentric Bearing |
| US9506541B2 (en) * | 2010-05-05 | 2016-11-29 | Robert Bosch Gmbh | Eccentric bearing |
| CN105408645A (en) * | 2013-08-12 | 2016-03-16 | 舍弗勒技术股份两合公司 | Non-slip rolling bearing |
| CN105408645B (en) * | 2013-08-12 | 2018-06-19 | 舍弗勒技术股份两合公司 | Non-slip rolling bearing |
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