JP2003314561A - Ball bearing - Google Patents
Ball bearingInfo
- Publication number
- JP2003314561A JP2003314561A JP2002115666A JP2002115666A JP2003314561A JP 2003314561 A JP2003314561 A JP 2003314561A JP 2002115666 A JP2002115666 A JP 2002115666A JP 2002115666 A JP2002115666 A JP 2002115666A JP 2003314561 A JP2003314561 A JP 2003314561A
- Authority
- JP
- Japan
- Prior art keywords
- ball
- ball bearing
- inner ring
- grease
- cage
- 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
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
(57)【要約】
【課題】 高温、高荷重、高速回転と言った厳しい条件
で使用される転がり軸受の寿命延長を図る。
【解決手段】 内輪、外輪両軌道2、4のうち、少なく
とも運転時に玉7の転動面との間に油膜の形成されにく
い、回転側軌道の中心線平均粗さσ1 を0.01〜0.
05μmRaとし、且つ、この回転側軌道のスキューネ
スRskを−1〜−5とする。これにより、特に、高速回
転時にも、上記回転側軌道と玉の転動面との間に油膜が
形成され易くなる様にして、上記課題を解決する。
(57) [Summary] [PROBLEMS] To extend the life of a rolling bearing used under severe conditions such as high temperature, high load and high speed rotation. SOLUTION: Of the inner and outer races 2, 4, a center line average roughness σ 1 of a rotating raceway, in which an oil film is less likely to be formed at least on a rolling surface of a ball 7 during operation, from 0.01 to 0.01. 0.
The skewness Rsk of this rotation-side orbit is set to -1 to -5. This solves the above-mentioned problem, in particular, such that an oil film is easily formed between the rotation-side orbit and the rolling surface of the ball even during high-speed rotation.
Description
【0001】[0001]
【発明の属する技術分野】本発明は、例えば、工作機械
や汎用モータ、或は電気自動車(EV)、ハイブリッド
車(HEV)、ベルト式無段変速機等の各種機械装置の
回転支持部分に組み込まれて、高荷重、高温、高速回転
と言った過酷な条件で使用される玉軸受の改良に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is incorporated in a rotation supporting portion of various machine devices such as machine tools, general-purpose motors, electric vehicles (EV), hybrid vehicles (HEV), belt type continuously variable transmissions, and the like. And to improve ball bearings used under severe conditions such as high load, high temperature, and high speed rotation.
【0002】[0002]
【従来の技術】各種機械装置の回転支持部分に玉軸受を
組み込む事が行なわれているが、これら各種機械装置の
耐久性及び信頼性を十分に確保する為には、上記回転支
持部分に組み込んだ玉軸受の寿命を十分に確保する必要
がある。この為に従来から、この玉軸受を構成する複数
個の玉を設置した空間内に十分な量の潤滑剤(油、グリ
ース)を供給又は封入し、この潤滑剤によりこれら各玉
と内輪、外輪両軌道との転がり接触部を潤滑する事が行
なわれている。この場合に、上記玉軸受の長寿命化を十
分に図れる様にする為には、上記転がり接触部での潤滑
状態を良好にする事が重要である。即ち、上記玉軸受の
寿命と上記転がり接触部での潤滑状態との間には、密接
な関係がある。2. Description of the Related Art Ball bearings have been incorporated into rotation supporting portions of various mechanical devices. In order to ensure the durability and reliability of these various mechanical devices, they are incorporated into the rotary supporting portions. It is necessary to secure a sufficient life of the ball bearing. For this reason, conventionally, a sufficient amount of lubricant (oil, grease) is supplied or enclosed in the space where a plurality of balls constituting this ball bearing are installed, and these lubricants, inner rings, and outer rings are provided by this lubricant. Lubrication of the rolling contact part with both tracks is performed. In this case, in order to sufficiently extend the life of the ball bearing, it is important to improve the lubrication condition at the rolling contact portion. That is, there is a close relationship between the life of the ball bearing and the lubrication state at the rolling contact portion.
【0003】この事から、上記玉軸受の寿命を評価する
際の指標として従来より、油膜パラメータΛと言う概念
が用いられている{例えば「転がり軸受工学(日本精工
株式会社 転がり軸受工学編集委員会編)」(株式会社
養賢堂、昭和50年7月10日第1版発行)p178参
照}。この油膜パラメータΛは、転がり接触部での潤滑
状態の良否の程度を示すもので、次の(1)式で表され
る。
Λ=hmin /√(hr1 2 +hr2 2 )
≒hmin /1.15√(σ1 2+σc 2) −−−−−(1)
この(1)式中、hmin は、互いに転がり接触する2面
間(上記玉軸受を構成する軌道と玉の転動面との間)の
最小油膜厚さを、hr1は、互いに転がり接触する2面の
うちの一方の面(上記軌道)の自乗平均粗さを、h
r2は、同じく他方の面(上記玉の転動面)の自乗平均粗
さを、σ1 は、上記一方の面(上記軌道)の中心線平均
粗さを、σc は、上記他方の面(上記玉の転動面)の中
心線平均粗さを、それぞれ表している。From this fact, the concept of oil film parameter Λ has been used as an index for evaluating the life of the ball bearings {for example, "Rolling bearing engineering (Nippon Seiko Co., Ltd. Rolling Bearing Engineering Editorial Committee Ed.) "(Yokendo Co., Ltd., published on July 10, 1975, 1st edition) p178. The oil film parameter Λ indicates the quality of the lubrication state at the rolling contact portion, and is expressed by the following equation (1). Λ = h min / √ (h r1 2 + h r2 2 ) ≈h min /1.15 √ (σ 1 2 + σ c 2 ) −−−−− (1) In this equation (1), h min are mutually The minimum oil film thickness between two surfaces in rolling contact (between the raceway forming the ball bearing and the rolling surface of the ball), h r1 is one of the two surfaces in rolling contact with each other (the raceway described above). ) Root mean square roughness, h
r2 is the root mean square roughness of the other surface (rolling surface of the ball), σ 1 is the center line average roughness of the one surface (orbit), and σ c is the other surface. The center line average roughness of (the rolling surface of the ball) is shown.
【0004】上記(1)式より、油膜パラメータΛの値
が大きい程上記玉軸受を構成する軌道と玉の転動面との
間に油膜が厚く形成され、結果としてこの玉軸受の寿命
が長くなる事が分かる。又、この様な油膜パラメータΛ
は、その値が3以下(Λ≦3)の場合に、潤滑状態が不
良と考えられ、玉軸受の寿命を十分に確保できない事が
知られている。又、上記(1)式より、上記軌道と上記
玉の転動面との中心線平均粗さσ1 、σc を小さくすれ
ば、上記油膜パラメータΛの値を大きくでき、結果とし
て上記玉軸受の寿命を長くできる事が分かる。この為、
従来から、上記軌道と上記玉の転動面とを滑らかな面に
加工する事により、これら軌道と玉の転動面との中心線
平均粗さσ1 、σc を小さくする事が行なわれている。From the above equation (1), the larger the value of the oil film parameter Λ, the thicker the oil film is formed between the raceway forming the ball bearing and the rolling surface of the ball, and as a result, the life of the ball bearing is longer. I understand that. In addition, such an oil film parameter Λ
It is known that when the value is 3 or less (Λ ≦ 3), the lubrication state is considered to be poor, and the life of the ball bearing cannot be sufficiently secured. Further, from the equation (1), if the center line average roughness σ 1 , σ c between the raceway and the ball rolling surface is reduced, the value of the oil film parameter Λ can be increased, and as a result, the ball bearing. You can see that you can extend the life of the. Therefore,
Conventionally, the center line average roughness σ 1 , σ c between the raceway and the ball rolling surface has been reduced by processing the raceway and the ball rolling surface into smooth surfaces. ing.
【0005】又、玉軸受の寿命延長を図る従来技術とし
て、特公平5−32602号公報には、「0.05μm
Ra<玉(鋼球)の表面粗さ<軌道(転走面)の表面粗
さ」と言う関係で玉の表面粗さを軌道の表面粗さに近づ
ける事により、これら玉と軌道との転がり接触部に油膜
が形成され易くなる様にし、これにより、この玉の温度
上昇を抑えてこの玉の転動面に剥離を生じにくくする技
術が記載されている。同じく、特許第2508178号
公報には、内輪、外輪両軌道と転動体の転動面とのう
ち、少なくとも外輪軌道(静止側軌道)に多数の溝状凹
部を形成すると共に、この外輪軌道のうちこれら各溝状
凹部を除く部分の表面粗さを0.08μmRa以下とす
る事により、上記転動体の滑り運動を抑制し、且つ、上
記各溝状凹部を潤滑油溜りとして機能させる事により転
がり接触部の潤滑状態を良好に保持する技術が記載され
ている。As a conventional technique for extending the life of a ball bearing, Japanese Patent Publication No. 5-32602 discloses "0.05 μm.
Ra <ball (steel ball) surface roughness <raceway (rolling surface) surface roughness ”, so that the ball surface roughness approaches the raceway surface roughness, the rolling of these balls and raceway A technique is described in which an oil film is easily formed on the contact portion, thereby suppressing the temperature rise of the ball and making it difficult to cause peeling on the rolling surface of the ball. Similarly, in Japanese Patent No. 2508178, a large number of groove-shaped recesses are formed in at least the outer ring raceway (stationary side raceway) among the inner ring and outer ring raceways and the rolling surfaces of the rolling elements. By setting the surface roughness of the portion excluding these groove-shaped recesses to 0.08 μmRa or less, the sliding motion of the rolling elements is suppressed, and the groove-shaped recesses function as a lubricating oil reservoir to make rolling contact. A technique for maintaining a good lubrication state of a part is described.
【0006】[0006]
【発明が解決しようとする課題】ところで、グリースを
封入した玉軸受の場合、一般に、この玉軸受の転がり接
触部で焼き付きが発生する事なく、この玉軸受を長時間
安全に運転できる限界のdm n値[dm {玉列の平均直
径(mm)}と、n{玉軸受の回転速度(min-1 )}との
積]は、60万dm n程度とされている。これに対し、
近年、例えば電気自動車、ハイブリッド車、ベルト式無
段変速機等の分野では、これら各機械装置の高性能化に
伴い、これら各機械装置の回転支持部分に組み込むグリ
ースを封入した玉軸受に対して、そのdm n値を60万
dm nよりも大きくする事が要求されつつある。この場
合、この玉軸受を構成する軌道と玉の転動面との中心線
平均粗さσ1 、σc を小さくすると言った従来の方法を
採用するだけでは、当該要求に応える事が難しい。By the way, in the case of a ball bearing filled with grease, generally, there is no seizure in the rolling contact portion of the ball bearing, and the limit d which allows safe operation of the ball bearing for a long time. The m n value [d m {average diameter of ball row (mm)} and n {rotational speed of ball bearing (min −1 )}] is about 600,000 d m n. In contrast,
In recent years, for example, in the fields of electric vehicles, hybrid vehicles, belt-type continuously variable transmissions, etc., as the performance of each of these mechanical devices has improved, ball bearings filled with grease to be incorporated in the rotation supporting portion of each of these mechanical devices have been used. However, it is demanded that the d m n value be larger than 600,000 d m n. In this case, it is difficult to meet the demand only by adopting the conventional method of reducing the center line average roughness σ 1 and σ c between the raceway and the ball rolling surface that compose the ball bearing.
【0007】又、前述の特公平5−32602号公報に
記載された発明の場合には、玉軸受を構成する軌道及び
玉の表面粗さが0.05μmRaよりも大きい。この
為、この玉軸受を60万dm nを越える様な高速回転で
運転する場合に、振動が増大して音響問題(騒音)が発
生したり、或は寿命を十分に確保できなくなる事が予想
される。又、前述の特許第2508178号公報に記載
された発明の場合には、内輪軌道に就いての最適な表面
粗さ等が示されていない。これに対し、ラジアル玉軸受
の場合、円周方向に関する形状が凹である外輪軌道より
も、円周方向に関する形状が凸である内輪軌道の方が、
凸面である玉の転動面との接触面積が小さくなる。更
に、玉軸受の運転時には、遠心力によりグリースが外輪
軌道に集まる傾向となる。この為、一般に、外輪軌道よ
りも内輪軌道の方が、玉の転動面との間に油膜が形成さ
れにくくなる。従って、この様に玉の転動面との間に油
膜が形成されにくい内輪軌道に就いての最適な表面粗さ
等が示されていない、上記特許第2508178号公報
に記載された発明の場合には、やはり玉軸受を60万d
m nを越える様な高速回転で運転する場合に、振動が増
大して音響問題が発生したり、或は寿命を十分に確保で
きなくなる事が予想される。この結果、これら各公報に
記載された発明によっては、グリースを封入した玉軸受
の限界のdm n値を増大させると言った要求に応える事
が難しいと考えられる。Further, in the above-mentioned Japanese Patent Publication No. 5-32602,
In the case of the described invention, the raceway that constitutes the ball bearing and
The surface roughness of the balls is larger than 0.05 μmRa. this
Therefore, this ball bearing is 600,000 dm With a high speed rotation that exceeds n
When driving, vibration increases and acoustic problems (noise) occur.
It is expected that it will not live or that it will not be possible to secure a sufficient life
To be done. Also, described in the above-mentioned Japanese Patent No. 2508178
In the case of the claimed invention, the optimum surface for the inner raceway
Roughness is not shown. On the other hand, radial ball bearings
In the case of, from the outer ring raceway whose shape in the circumferential direction is concave
Also, the inner ring raceway, which has a convex shape in the circumferential direction,
The contact area of the convex ball with the rolling surface is reduced. Change
In addition, during operation of the ball bearings, centrifugal force causes grease to
It tends to gather in orbit. Therefore, in general,
An oil film is formed between the ball raceway and the inner ring raceway.
It becomes difficult to be damaged. Therefore, in this way, there is no oil between the rolling surface of the ball.
Optimum surface roughness for inner ring raceways where film is hard to form
No. 2,508,178, which is not shown.
In the case of the invention described in 1.
m Vibration increases when operating at high speeds exceeding n.
Sound problems may occur, or the life may be long enough.
It is expected that it will stop. As a result, in each of these publications
Depending on the described invention, a grease-filled ball bearing
The limit of dm Meet the demand for increasing the n value
Is considered difficult.
【0008】一方、例えば自動車用変速機の周辺部分
等、運転時の温度が160℃を越える様な部位で使用さ
れるグリースを封入した玉軸受の場合、複数個の玉を保
持する為の保持器としては、熱変形を起こし易い合成樹
脂製のものを使用できない為、熱変形しにくい鋼製のも
のを使用する。ところが、この様な鋼製の保持器を組み
込んだ玉軸受の運転時に、グリースの流動性が悪く、こ
の保持器の表面と上記複数個の玉の転動面との摺接部で
このグリースの油膜切れが起こると、この摺接部で上記
保持器の表面から鉄摩耗粉が発生し易くなる。この様に
して発生した鉄摩耗粉は、上記複数個の玉を設置した空
間内に封入したグリース中に混入して、このグリースの
酸化を促進させ、このグリースの寿命を短くさせる。
又、この様にしてグリースの寿命が短くなる割合は、こ
のグリース中に混入する鉄摩耗粉の量が多くなる程大き
くなる。これに対し、上記鋼製の保持器が汎用のもので
ある場合に、この保持器を組み込んだ玉軸受を60万d
m nを越える様な高速回転で運転すると、上述の様にし
て発生する鉄摩耗粉の量が多くなると考えられる。従っ
て、グリースを封入した玉軸受に組み込む保持器を鋼製
とする場合に、この玉軸受の限界のdm n値の増大を図
る場合には、上記鉄摩耗粉の発生を防止する手段を用意
する事が好ましい。On the other hand, in the case of a ball bearing filled with grease which is used in a portion where the temperature during operation exceeds 160 ° C., for example, in the peripheral portion of a transmission for automobiles, a holding for holding a plurality of balls. As the container, one made of synthetic resin that is easily deformed by heat cannot be used, so one made of steel that is not easily deformed by heat is used. However, during operation of a ball bearing incorporating such a steel cage, the fluidity of the grease is poor, and this grease is not formed at the sliding contact portion between the surface of this cage and the rolling surfaces of the plurality of balls. When the oil film runs out, iron abrasion powder is easily generated from the surface of the cage at the sliding contact portion. The iron abrasion powder thus generated mixes with the grease enclosed in the space where the plurality of balls are installed, accelerates the oxidation of the grease, and shortens the life of the grease.
Further, the rate at which the life of the grease is shortened in this way becomes larger as the amount of iron wear powder mixed in the grease increases. On the other hand, when the above steel cage is a general-purpose type, a ball bearing incorporating this cage has 600,000 d
It is considered that the amount of iron abrasion powder generated as described above increases when the engine is operated at a high speed rotation exceeding mn. Therefore, when the cage incorporated in the ball bearing containing grease is made of steel, in order to increase the limit d m n value of the ball bearing, a means for preventing the generation of iron abrasion powder is prepared. It is preferable to do.
【0009】尚、以上に述べた様な問題は、グリースを
封入した玉軸受に限らず、潤滑剤として油を使用する玉
軸受にも当てはまり、何れの場合も問題を解決し得る手
段の提供が望まれている。本発明の玉軸受は、この様な
事情に鑑みて発明したものである。The above-mentioned problems are not limited to ball bearings filled with grease, but are also applicable to ball bearings that use oil as a lubricant, and in any case, it is possible to provide means for solving the problems. Is desired. The ball bearing of the present invention was invented in view of such circumstances.
【0010】[0010]
【課題を解決するための手段】本発明の玉軸受は、外周
面に内輪軌道を形成した内輪と、内周面に外輪軌道を形
成した外輪と、これら内輪軌道と外輪軌道との間に転動
自在に設けられた複数個の玉とを備える。特に、本発明
の玉軸受に於いては、上記内輪軌道と上記外輪軌道との
うち、少なくとも内輪軌道の中心線平均粗さσ1 を0.
01〜0.05μmRaとし、且つ、この内輪軌道のス
キューネスRskを−1〜−5としている。A ball bearing according to the present invention comprises an inner ring having an inner ring raceway formed on an outer peripheral surface thereof, an outer ring having an outer ring raceway formed on an inner peripheral surface thereof, and a rolling member between the inner ring raceway and the outer ring raceway. And a plurality of movably provided balls. Particularly, in the ball bearing of the present invention, at least the center line average roughness σ 1 of the inner ring raceway and the outer ring raceway is set to 0.
The inner ring raceway has a skewness Rsk of -1 to -5.
【0011】尚、上記スキューネスRskとは、図2に示
す様に、対象となる面の断面曲線の平均線に対する振幅
分布曲線の上下非対称性を示す量で、次の(2)式で表
される。The above-mentioned skewness R sk is an amount showing the vertical asymmetry of the amplitude distribution curve with respect to the average line of the sectional curve of the target surface, as shown in FIG. To be done.
【数1】
この(2)式中、Rq は、対象となる面の自乗平均粗さ
を、nは、上記断面曲線中の試料点の数を、Yi は、こ
れら各試料点の上記平均線からの偏差を、それぞれ示
す。[Equation 1] In this equation (2), R q is the root mean square roughness of the target surface, n is the number of sample points in the cross-section curve, and Y i is the average line of each of these sample points. The deviations are shown respectively.
【0012】又、上述の様に、上記各軌道の中心線平均
粗さσ1 を0.01〜0.05μmRaとし且つスキュ
ーネスRskを−1〜−5とする為に、これら各軌道に、
例えばプラトー加工と呼ばれるクロス目の超仕上げ加工
を施す。即ち、対象となる軌道に超仕上げ加工を、互い
に異なる2方向に就いて行なう事により、この軌道に網
目状の微細な加工目(クロス目)を形成する。この場合
に好ましくは、互いにクロスさせる加工目の二等分線の
方向と当該軌道の円周方向とを一致させる。Further, as described above, in order to set the center line average roughness σ 1 of each orbit to 0.01 to 0.05 μmRa and the skewness R sk to −1 to −5,
For example, a cross finish superfinishing process called plateau processing is performed. That is, by performing superfinishing on the target track in two different directions, a fine mesh-like pattern (cross) is formed on this track. In this case, it is preferable that the direction of the bisector of the machined lines to be crossed with each other and the circumferential direction of the track be matched.
【0013】尚、実開昭61−23520号公報には、
ころ軸受を構成する軌道に上述したプラトー加工を施す
事により、この軌道ところとの転がり接触部の潤滑状態
を良好にする技術が記載されている。しかしながら、玉
軸受の場合にはころ軸受の場合に比べて、軌道の表面粗
さを格段に良く加工する事ができる。この為、玉軸受の
場合には、転がり接触部の潤滑状態を良好にする手段と
して、軌道の表面粗さを良くする方法を採用するのが主
流になっており、特に、自動車用の玉軸受等、高速回
転、高荷重と言った厳しい条件で使用される、内径が2
5mmを越えるサイズの玉軸受では、これまで軌道にプラ
トー加工を施す技術が採用される事はなかった。In addition, Japanese Utility Model Publication No. 61-23520 discloses that
A technique is disclosed in which the raceway forming the roller bearing is subjected to the above-described plateau process to improve the lubrication state of the rolling contact portion with the raceway. However, in the case of the ball bearing, the surface roughness of the race can be machined far better than in the case of the roller bearing. For this reason, in the case of ball bearings, a method of improving the surface roughness of the raceways has become the mainstream as a means for improving the lubrication state of the rolling contact portion. Used under severe conditions such as high-speed rotation and high load, the inner diameter is 2
For ball bearings with a size of more than 5 mm, the technology to plateau the raceway has never been adopted.
【0014】又、請求項2に記載した玉軸受は、上記複
数個の玉を保持する為の鋼製の保持器(例えば、もみ抜
き保持器、波形プレス保持器等)を備える。そして、こ
の保持器に軟窒化処理を施す事により、この保持器の表
面のうち、少なくとも運転時に上記各玉の転動面と摺接
する部分に、厚さ3〜20μmの窒化層を形成してい
る。A ball bearing according to a second aspect of the present invention includes a steel cage (for example, a machined cage, a corrugated press cage, etc.) for holding the plurality of balls. Then, by performing a soft nitriding treatment on this cage, a nitride layer having a thickness of 3 to 20 μm is formed on at least a portion of the surface of the cage that is in sliding contact with the rolling surface of each ball during operation. There is.
【0015】又、請求項3に記載した玉軸受は、上記複
数個の玉の設置部を潤滑する潤滑剤として、グリースを
使用するものである。Further, in the ball bearing according to the third aspect, grease is used as a lubricant for lubricating the installation portion of the plurality of balls.
【0016】又、本発明を実施する場合には、音響問題
の発生を防止する為、上記各玉の転動面の中心線平均粗
さσc を、上記各軌道の中心線平均粗さσ1 よりも小さ
く(例えば、0.002〜0.010μmRa程度に)
するのが好ましい。Further, in the case of implementing the present invention, in order to prevent the occurrence of acoustic problems, the center line average roughness σ c of the rolling surface of each ball is set to the center line average roughness σ of each track. Less than 1 (for example, about 0.002-0.010 μmRa)
Preferably.
【0017】[0017]
【作用】上述の様に、内輪軌道と外輪軌道とのうち、少
なくとも内輪軌道の中心線平均粗さσ1 を0.01〜
0.05μmRaとし、且つ、この内輪軌道のスキュー
ネスRskを−1〜−5とした本発明の場合、この内輪軌
道の粗さ形状は、図3(A)に示す様に、表面(図3の
上面)が平滑で、しかも、全体に潤滑剤(油、グリー
ス)溜りとなる微細且つ適当な深さの溝が形成された状
態となっている。この為、前述した様に油膜が形成され
にくいとされる内輪軌道と玉の転動面との間に油膜を形
成し易くでき、しかも、これら内輪軌道と玉の転動面と
の間で油膜切れが起こり易い高速回転時に、上記潤滑剤
溜りから潤滑剤を供給して、油膜切れが起こるのを有効
に防止できる。この結果、玉軸受(特に、請求項3に記
載した様なグリースを封入した玉軸受)の寿命延長と限
界のdm n値の増大とを図れる。As described above, of the inner ring raceway and the outer ring raceway, at least the center line average roughness σ 1 of the inner ring raceway is 0.01 to
In the case of the present invention in which the inner ring raceway has a skewness R sk of 0.05 μmRa and a skewness R sk of -1 to -5, the roughness profile of the inner ring raceway is as shown in FIG. The upper surface) is smooth, and a groove having a fine and appropriate depth that serves as a lubricant (oil, grease) reservoir is formed over the entire surface. For this reason, as described above, it is easy to form an oil film between the inner ring raceway and the rolling surface of the ball, where it is difficult to form an oil film, and the oil film is formed between these inner ring raceway and the rolling surface of the ball. It is possible to effectively prevent the occurrence of oil film breakage by supplying the lubricant from the lubricant reservoir at the time of high-speed rotation where breakage easily occurs. As a result, it is possible to extend the life of the ball bearing (particularly, the ball bearing containing grease as described in claim 3) and increase the limit d m n value.
【0018】これに対し、軌道の中心線平均粗さσ1 だ
けを良くして、スキューネスRskを規制していない従来
の玉軸受の場合、この軌道の粗さ形状は、図3(B)に
示す様に、基準となる平均線に対して上下ほぼ対象な形
状になっており、潤滑剤溜りとして機能する微細な溝が
十分には確保されない状態となっている。この為、本発
明の様な寿命延長等の効果を望む事は難しい。On the other hand, in the case of the conventional ball bearing in which only the center line average roughness σ 1 of the race is improved and the skewness R sk is not regulated, the roughness shape of this race is shown in FIG. 3 (B). As shown in, the shape is substantially symmetrical with respect to the reference average line, and the fine grooves functioning as a lubricant reservoir are not sufficiently secured. For this reason, it is difficult to obtain the effects of the present invention such as extending the life.
【0019】又、請求項2に記載した玉軸受の場合に
は、高速回転時に、潤滑剤(例えばグリース)の流動性
が悪く、保持器の表面と玉の転動面との摺接部で油膜切
れが起こった場合でも、この摺接部で上記保持器の表面
から鉄摩耗粉が生じるのを有効に防止できる。この為、
この鉄摩耗粉が潤滑剤中に混入する事に基づく、この潤
滑剤の早期劣化を有効に防止できる。従って、やはり、
玉軸受(特に、請求項3に記載した様なグリースを封入
した玉軸受)の寿命延長と限界のdm n値の増大とを図
れる。Further, in the case of the ball bearing according to the second aspect of the invention, the fluidity of the lubricant (eg grease) at the time of high speed rotation is poor, and at the sliding contact portion between the surface of the cage and the rolling surface of the ball. Even if the oil film runs out, it is possible to effectively prevent iron abrasion powder from being generated from the surface of the cage at the sliding contact portion. Therefore,
It is possible to effectively prevent early deterioration of the lubricant due to mixing of the iron wear powder into the lubricant. Therefore,
It is possible to extend the life of the ball bearing (in particular, the ball bearing containing grease as described in claim 3) and increase the limit d m n value.
【0020】[0020]
【実施例】本発明の効果を確認する為に行なった実験に
就いて説明する。この実験では、本発明の玉軸受に該当
する10種類の試料(実施例1〜10)と、従来の玉軸
受に該当する10種類の試料(比較例1〜10)とに就
いて、それぞれ所定時間、所定の条件で運転を行ない、
これら各試料に損傷が発生するか否かを調べた。EXAMPLE An experiment conducted for confirming the effect of the present invention will be described. In this experiment, 10 types of samples corresponding to the ball bearing of the present invention (Examples 1 to 10) and 10 types of samples corresponding to conventional ball bearings (Comparative Examples 1 to 10) were each given a predetermined value. Drive for a certain period of time,
It was examined whether damage was generated in each of these samples.
【0021】本実験では、上記各試料(実施例1〜1
0、比較例1〜10)となる玉軸受として、図1に示す
様な深溝型の玉軸受1を使用した。この玉軸受1は、外
周面に深溝型の内輪軌道2を有する内輪3と、内周面に
深溝型の外輪軌道4を有する外輪5と、これら内輪軌道
2と外輪軌道4との間に保持器6により保持した状態で
転動自在に設けられた複数個の玉7とを備える。尚、図
示の例では、上記保持器6として、鋼製の波形プレス保
持器を組み付けている。又、上記各玉7を設置した空間
の両端開口を、それぞれ非接触型のシールドリング8、
8により塞ぐと共に、この空間内に潤滑用のグリースを
封入している。又、本実験では、この様な玉軸受1とし
て、JIS呼び番号6206(内径30mm、外径62m
m、幅16mm)で表されるものを使用した。この玉軸受
1は、玉列の平均直径dm が46.5mmであり、カタロ
グ許容回転数が、油潤滑で13000min-1 であり、グ
リース潤滑で11000min-1 である為、これらに基づ
くグリース潤滑での限界のdmn値は、約51万dm n
である。他の諸元は、以下の通りである。
軸受材料 : 軸受鋼2種
内輪3及び外輪5の表面硬さ : HRC 58〜63
内輪3及び外輪5の残留オーステナイト量 : 0.05〜15%
玉7の表面硬さ : HRC 62〜64
シールドリング8 : ニトリルシール
グリース : リチウム石鹸系グリース(40℃:26cSt、100℃:5
cSt)を軸受空間容積の20%封入In this experiment, each of the above samples (Examples 1 to 1) was used.
0, Comparative Examples 1 to 10), a deep groove type ball bearing 1 as shown in FIG. 1 was used. This ball bearing 1 holds between an inner ring 3 having a deep groove type inner ring raceway 2 on the outer peripheral surface, an outer ring 5 having a deep groove type outer ring raceway 4 on the inner peripheral surface, and these inner ring raceway 2 and outer ring raceway 4 It is provided with a plurality of balls 7 which are rollably provided while being held by the container 6. In the illustrated example, a steel corrugated press cage is assembled as the cage 6. In addition, the openings at both ends of the space in which the balls 7 are installed are respectively provided with non-contact type shield rings 8,
It is closed by 8, and grease for lubrication is enclosed in this space. In addition, in this experiment, as such a ball bearing 1, JIS No. 6206 (inner diameter 30 mm, outer diameter 62 m
m, width 16 mm) was used. The ball bearing 1 is the mean diameter d m of the ball row is 46.5 mm, catalog allowable rotational speed, a 13000Min -1 in oil lubrication, because it is 11000Min -1 with grease lubrication, grease lubrication based on these The limit d m n value at is about 510,000 d m n
Is. Other specifications are as follows. Bearing material: surface hardness of the bearing steel two inner ring 3 and the outer ring 5: the amount of retained austenite of H R C 58-63 inner ring 3 and the outer ring 5: 0.05 to 15% ball 7 of surface hardness: H R C 62 ~ 64 Shield ring 8: Nitrile seal grease: Lithium soap grease (40 ° C: 26 cSt, 100 ° C: 5 cSt) filled 20% of the bearing space volume.
【0022】又、上記各試料(実施例1〜10、比較例
1〜10)とも、運転時に回転側軌道となる内輪軌道2
と、静止側軌道となる外輪軌道4との、互いの中心線平
均粗さσ1 及びスキューネスRskを同じにした。又、上
記各試料(実施例1〜10、比較例1〜10)とも、玉
7の転動面の中心線平均粗さを0.005μmRaと
し、更に、保持器6として、次のA〜Cのうちの何れか
のものを選択使用した。
A:鋼製の波形プレス保持器(表面処理なし)
B:鋼製の波形プレス保持器{軟窒化処理により、表面
全体に厚さ10μmの窒化層を形成したもの(特開20
01−90734号公報に記載されたもの)}
C:ナイロン66(ポリアミド樹脂)製の冠型保持器In addition, in each of the above-mentioned samples (Examples 1 to 10 and Comparative Examples 1 to 10), the inner ring raceway 2 which becomes the rotation side raceway during operation.
And the outer ring raceway 4 which is the stationary side raceway have the same center line average roughness σ 1 and skewness R sk . Further, in each of the above-mentioned samples (Examples 1 to 10 and Comparative Examples 1 to 10), the center line average roughness of the rolling surface of the ball 7 was set to 0.005 μmRa, and further, as the cage 6, the following A to C were used. Any one of them was selected and used. A: Corrugated press cage made of steel (without surface treatment) B: Corrugated press cage made of steel {A nitriding layer having a thickness of 10 μm formed on the entire surface by soft nitriding treatment (Japanese Patent Application Laid-Open No. 20
No. 01-90734)} C: Nylon 66 (polyamide resin) crown type cage
【0023】本実験では、上記各試料(実施例1〜1
0、比較例1〜10)を、それぞれ前記外輪5を静止輪
とし、前記内輪3を回転輪として運転した。具体的な試
験条件は、以下の通りである。
荷重条件 : P(負荷荷重)/C(動定格荷重)=0.25
転がり接触部での最大接触面圧Pmax : 3GPa
回転速度 : 20000min-1 (93万dm n)
軸受温度 : 100℃(一定となる様に軸受用ハウジングを冷却)In this experiment, each of the above samples (Examples 1 to 1)
0, Comparative Examples 1 to 10) were each operated with the outer wheel 5 as a stationary wheel and the inner wheel 3 as a rotating wheel. The specific test conditions are as follows. Load condition: P (load load) / C (dynamic load rating) = 0.25 Maximum contact surface pressure at rolling contact part P max : 3 GPa Rotation speed: 20000 min -1 (930,000 d m n) Bearing temperature: 100 ° C (Cooling the bearing housing to keep it constant)
【0024】又、上述の様な試験条件を設定した場合の
前記玉軸受1の計算寿命(剥離寿命)L10は53時間で
あり、グリース寿命はこれ以上であると考えられる。こ
の為、本実験では、上記各試料(実施例1〜10、比較
例1〜10)の運転の打ち切り時間を、上記計算寿命L
10の約2倍の100時間(一部は200時間)とした。
但し、100時間に到達する前に、上記各試料(実施例
1〜10、比較例1〜10)の振動の大きさが初期振動
の大きさの5倍まで上昇した場合には、その時点で運転
を中断し、焼き付きや剥離の有無を確認した。又、この
様な実験を、上記各試料(実施例1〜10、比較例1〜
10)に就いて、それぞれ10個ずつ行なった。実験の
結果を、以下の表1に示す。When the above test conditions are set, the calculated life (peeling life) L 10 of the ball bearing 1 is 53 hours, and the grease life is considered to be longer than this. Therefore, in this experiment, the operation termination time of each of the samples (Examples 1 to 10 and Comparative Examples 1 to 10) was calculated as
It was set to be 100 times (some 200 hours), which is about twice as much as 10.
However, when the magnitude of vibration of each of the above-mentioned samples (Examples 1 to 10 and Comparative Examples 1 to 10) increased to 5 times the magnitude of initial vibration before reaching 100 hours, at that time point. The operation was interrupted, and the presence or absence of seizure or peeling was confirmed. In addition, such an experiment was performed on each of the samples (Examples 1 to 10 and Comparative Examples 1 to 1).
For 10), we did 10 each. The results of the experiment are shown in Table 1 below.
【表1】 [Table 1]
【0025】前述の試験条件で示した様に、本実験で
は、上記各試料(実施例1〜10、比較例1〜10)
を、前述したカタログに基づく限界のdm n値(51万
dm n)を越える、93万dm nの条件で運転した。と
ころが、上記表1に示した結果より、実施例2、3、
5、6、7、9、10に就いては、それぞれ10個の試
料全部が、運転時間が100時間を越え、更に200時
間に到達しても、内輪、外輪各軌道2、4及び玉7の転
動面に剥離の発生が認められなかった。この様にグリー
スを封入した玉軸受の耐久性を向上させる事ができた理
由は、前述した様に、内輪、外輪各軌道2、4(特に内
輪軌道2)の中心線平均粗さσ1 を0.01〜0.05
μmRaの範囲に収め、且つ、上記各軌道2、4のスキ
ューネスRskを−1〜−5の範囲に収める事により、こ
れら各軌道2、4の粗さ形状を図3(A)に示す様な形
状にして、これら各軌道2、4と玉7との転がり接触部
にグリースの油膜を形成し易くし、且つ、この転がり接
触部で油膜切れが起こり易い高速回転時に、上記各軌道
2、4に形成されたグリース溜りからグリースを供給し
て、油膜切れが起こるのを有効に防止できた為であると
考えられる。更には、保持器6として前述したB又はC
のものを使用する事により、この保持器6の表面と上記
玉7の転動面との摺接部で鉄摩耗粉が発生する事を防止
して、この鉄摩耗粉の混入に基づくグリースの早期劣化
を防止できた為であると考えられる。As shown in the above-mentioned test conditions, in the present experiment, each of the above samples (Examples 1 to 10 and Comparative Examples 1 to 10)
Was operated under the condition of 930,000 d m n, which exceeds the limit d m n value (510,000 d m n) based on the above-mentioned catalog. However, from the results shown in Table 1 above, the results of Examples 2, 3,
As for 5, 6, 7, 9, and 10, all of the 10 samples each have inner and outer raceways 2, 4 and balls 7 even when the operating time exceeds 100 hours and reaches 200 hours. No peeling was observed on the rolling surface. As described above, the reason why the durability of the ball bearing filled with grease can be improved is that the center line average roughness σ 1 of each of the inner ring and outer ring raceways 2, 4 (in particular, the inner ring raceway 2) is 0.01-0.05
By keeping the skewness R sk of each of the orbits 2 and 4 within the range of -1 to -5 within the range of μmRa, the roughness shape of each of the orbits 2 and 4 is as shown in FIG. 3 (A). To facilitate the formation of an oil film of grease at the rolling contact portions between the orbits 2 and 4 and the balls 7, and at the time of high speed rotation at which the oil film is likely to run out at the rolling contact portions, It is considered that this is because the grease was supplied from the grease reservoir formed in 4 to effectively prevent the oil film from running out. Furthermore, the above-mentioned B or C as the cage 6 is used.
It is possible to prevent the generation of iron abrasion powder at the sliding contact portion between the surface of the cage 6 and the rolling surface of the ball 7 by using the one of It is considered that this is because the early deterioration could be prevented.
【0026】しかしながら、上記各実施例2、3、5、
6、7、9、10のうち、上記保持器6として合成樹脂
製の保持器Cを使用した実施例3、7、10に就いて
は、試験後、上記玉7を抱える保持器先端部に発熱によ
る損傷が確認された。この為、dm n値が80万dm n
を越える条件で運転する場合で、且つ、上記保持器6と
して合成樹脂製の保持器を使用する場合には、この保持
器6に発熱による損傷を発生させない様にする為に、軸
受温度が100℃以下となる環境を選んで使用するのが
好ましいと言える。However, in each of the above-mentioned Examples 2, 3, 5,
Of Examples 6, 7, 9 and 10, Examples 3, 7 and 10 in which the cage C made of synthetic resin was used as the cage 6 were used after the test at the tip of the cage holding the balls 7. Damage due to heat generation was confirmed. Therefore, the d m n value is 800,000 d m n
In the case of operating under the condition of exceeding the above condition and using a cage made of synthetic resin as the cage 6, in order to prevent the cage 6 from being damaged by heat generation, the bearing temperature is 100 It can be said that it is preferable to select and use an environment in which the temperature is not higher than ° C.
【0027】又、残りの実施例1、4、8に就いては、
それぞれ運転時間が100時間に到達する以前に、10
個中2〜3個の割合で焼き付きが発生したが、この様に
焼き付きが発生した時間のうち最も短い時間が、それぞ
れ53時間、55時間、67時間と、計算寿命である5
3時間以上であった為、やはり耐久性の向上を図れる事
が分かった。尚、これら各実施例1、4、8に就いて、
それぞれ100時間に到達する以前に、10個中2〜3
個の割合で焼き付きが発生した理由は、保持器6として
表面処理がなされていない、鋼製の保持器Aを使用した
事により、この保持器6の表面と玉7の転動面との摺接
部で鉄摩耗粉が発生し、この鉄摩耗粉がグリース中に混
入してこのグリースの酸化劣化を促進させた為であると
考えられる。Regarding the remaining Examples 1, 4, and 8,
Before each driving time reaches 100 hours, 10
Image sticking occurred at a rate of 2 to 3 pieces, and the shortest time of such image sticking was 53 hours, 55 hours, and 67 hours, respectively, which is the calculated life.
Since it was over 3 hours, it was found that the durability could be improved. Regarding each of these Examples 1, 4 and 8,
2-3 out of 10 before reaching 100 hours each
The reason why seizure occurred at the rate of the number of pieces was that the use of steel cage A, which was not surface-treated as cage 6, caused the sliding between the surface of cage 6 and the rolling surface of balls 7. It is considered that iron abrasion powder was generated at the contact portion, and this iron abrasion powder was mixed into the grease to promote the oxidative deterioration of the grease.
【0028】一方、比較例1〜7に就いては、それぞれ
保持器6として前述したA、B、Cのうちの何れかのも
のを使用し、内輪、外輪各軌道2、4の中心線平均粗さ
σ1を0.01〜0.05μmRaの範囲内に収めた
が、これら各軌道2、4のスキューネスRskを−1より
大きくした結果、それぞれ試料10個の全部が、計算寿
命である53時間よりも短い運転時間で焼き付いた。こ
の理由は、上記各軌道2、4の中心線平均粗さσ1 だけ
を良くしても、これら各軌道2、4のスキューネスRsk
を−1より大きくとすると、これら各軌道2、4の粗さ
形状が図3(B)に示す様になって、グリース溜りが形
成されにくくなり、高速回転時に上記各軌道2、4と玉
7との転がり接触部の潤滑状態を良好にできなくなる為
であると考えられる。On the other hand, in Comparative Examples 1 to 7, any one of the above-mentioned A, B, and C is used as the cage 6, and the center line average of the inner ring and outer ring raceways 2 and 4 is averaged. The roughness σ 1 was set within the range of 0.01 to 0.05 μmRa, but as a result of making the skewness R sk of each of these trajectories 2 and 4 larger than −1, all 10 samples each have a calculated life. It burned in less than 53 hours. The reason is that even if only the center line average roughness σ 1 of each of the trajectories 2 and 4 is improved, the skewness R sk of each of the trajectories 2 and 4 is increased.
Is larger than -1, the roughness shape of each of the tracks 2 and 4 becomes as shown in FIG. 3 (B), and it becomes difficult for a grease pool to be formed. It is considered that this is because the lubrication state of the rolling contact portion with No. 7 cannot be improved.
【0029】又、比較例8、9に就いては、保持器6と
して前述したA又はBのものを使用し、内輪、外輪各軌
道2、4のスキューネスRskを−1〜−5の範囲内に収
めたが、これら各軌道2、4の中心線平均粗さσ1 を
0.08μmRaと悪くした結果、それぞれ計算寿命で
ある53時間よりも短い運転時間で、10個中4〜5個
の割合で内輪軌道2に剥離が発生した。この理由は、上
記各軌道2、4のスキューネスRskだけを適正な範囲に
収めても、これら各軌道2、4の中心線平均粗さσ1 が
大きいと、dm n値が80万dm nを越える運転状態で
は振動が大きくなり、上記各軌道2、4(特に、油膜が
形成されにくいとされる内輪軌道2)と玉7の転動面と
の間で頻繁に金属接触が起こる為であると考えられる。Further, in Comparative Examples 8 and 9, the cage 6 of A or B described above was used, and the skewness R sk of each of the inner ring and outer ring raceways 2 and 4 was in the range of -1 to -5. However, as a result of deteriorating the center line average roughness σ 1 of each of these orbits 2 and 4 to 0.08 μmRa, 4 to 5 out of 10 running times were shorter than the calculated life of 53 hours. The peeling occurred on the inner ring raceway 2 at a rate of. The reason is that even if only the skewness R sk of each of the trajectories 2 and 4 is set within an appropriate range, if the center line average roughness σ 1 of each of the trajectories 2 and 4 is large, the d m n value is 800,000 d. In an operating state exceeding mn, the vibration becomes large, and metal contact frequently occurs between the raceways 2 and 4 (in particular, the inner ring raceway 2 where it is difficult to form an oil film) and the rolling surface of the ball 7. It is thought to be for the reason.
【0030】更に、残りの比較例10に就いては、内
輪、外輪各軌道2、4の中心線平均粗さが0.08μm
Raと悪く、しかもスキューネスRskが−1より大きい
為、振動の増大と潤滑不良とに基づき、計算寿命である
53時間よりも大幅に短い運転時間で、試料10個全部
で焼き付きが発生した。Further, in the remaining Comparative Example 10, the center line average roughness of the inner ring and outer ring raceways 2, 4 is 0.08 μm.
Since all of the 10 samples had seizures in a significantly shorter operating time than the calculated life of 53 hours, due to an increase in vibration and poor lubrication, the image quality was poor as Ra and the skewness R sk was larger than -1.
【0031】尚、上述した実施例では、潤滑剤としてグ
リースを使用した場合に就いて示したが、本発明は、潤
滑剤として低粘度の油を使用する場合でも、上述した実
験と同様の優れた効果が得られる事が、本発明者が行な
った実験により確認された。In the above-mentioned examples, the case where grease is used as the lubricant has been shown, but the present invention has the same excellent effect as in the above-mentioned experiment even when low-viscosity oil is used as the lubricant. It was confirmed by an experiment conducted by the present inventor that the above effect can be obtained.
【0032】尚、本発明を実施する場合、玉として窒化
珪素玉やアルミナ系のセラミック玉を使用すれば、玉軸
受全体としての軽量化を図れる事は勿論、高速回転時の
遠心力を小さくして、軌道の接触楕円の面積を小さくで
きる。この為、転がり接触部での発熱を抑える事がで
き、熱によるグリースの劣化を防止する事ができる。
又、上述した実施例では、潤滑用のグリースとしてリチ
ウム石鹸系のグリースを使用したが、これに代えて、エ
ーテル系のグリースや、流動性を向上させた耐熱グリー
スを使用し、又、ニトリルシールに代えて、アクリルや
弗素系の樹脂シールを使用すれば、更なる高温での使用
が可能となる。特にこれらの効果は、保持器としてポリ
アミド、ポリエーテルエーテルケトン(PEEK)、ポ
リフェニレンサルファド(PPS)を用いる場合に大き
く得られて、玉軸受(特に、グリースを封入した玉軸
受)の更なる寿命延長を図れる。In the case of carrying out the present invention, if a silicon nitride ball or an alumina ceramic ball is used as the ball, the weight of the ball bearing as a whole can be reduced and the centrifugal force during high speed rotation can be reduced. Thus, the area of the contact ellipse of the orbit can be reduced. Therefore, it is possible to suppress the heat generation at the rolling contact portion and prevent the grease from being deteriorated by heat.
Further, in the above-mentioned examples, the lithium soap grease was used as the lubricating grease, but instead of this, ether grease or heat resistant grease with improved fluidity was used, and the nitrile seal was used. If an acrylic or fluorine-based resin seal is used instead, it can be used at a higher temperature. In particular, these effects are greatly obtained when polyamide, polyetheretherketone (PEEK), and polyphenylene sulfide (PPS) are used as a cage, and further life of ball bearings (particularly ball bearings filled with grease) is improved. Can be extended.
【0033】[0033]
【発明の効果】本発明の玉軸受は、以上に述べた様に構
成され作用する為、寿命の延長と限界のdm n値の増大
とを図る事ができる。又、潤滑剤としてグリースを使用
する場合に特に顕著な効果を得られる。この為、この玉
軸受を組み込んだ各種機械装置の更なる性能向上に寄与
できる。Since the ball bearing of the present invention is constructed and operates as described above, it is possible to prolong the life and increase the limit d m n value. Further, a particularly remarkable effect can be obtained when grease is used as a lubricant. Therefore, it is possible to contribute to further improvement in the performance of various mechanical devices incorporating this ball bearing.
【図1】本発明の実施例を示す玉軸受の部分断面図。FIG. 1 is a partial sectional view of a ball bearing showing an embodiment of the present invention.
【図2】断面曲線とスキューネスRskとの関係を説明す
る為の線図。FIG. 2 is a diagram for explaining the relationship between a sectional curve and skewness R sk .
【図3】実施例と比較例との内輪軌道の断面形状を示す
線図。FIG. 3 is a diagram showing a cross-sectional shape of inner ring raceways of an example and a comparative example.
1 玉軸受 2 内輪軌道 3 内輪 4 外輪軌道 5 外輪 6 保持器 7 玉 8 シールドリング 1 ball bearing 2 Inner ring track 3 inner ring 4 Outer ring track 5 outer ring 6 cage 7 balls 8 Shield ring
Claims (3)
周面に外輪軌道を形成した外輪と、これら内輪軌道と外
輪軌道との間に転動自在に設けられた複数個の玉とを備
えた玉軸受に於いて、上記内輪軌道と上記外輪軌道との
うち、少なくとも内輪軌道の中心線平均粗さσ1 を0.
01〜0.05μmRaとし、且つ、この内輪軌道のス
キューネスRskを−1〜−5とした事を特徴とする玉軸
受。1. An inner ring having an inner ring raceway formed on an outer peripheral surface, an outer ring having an outer ring raceway formed on an inner peripheral surface, and a plurality of balls rotatably provided between the inner ring raceway and the outer ring raceway. Of the inner ring raceway and the outer ring raceway, at least the center line average roughness σ 1 of the inner ring raceway is set to 0.
The ball bearing is characterized in that the inner ring raceway has a skewness R sk of -1 to -5.
を備え、この保持器に軟窒化処理を施す事により、この
保持器の表面のうち、少なくとも運転時に上記各玉の転
動面と摺接する部分に、厚さ3〜20μmの窒化層を形
成した、請求項1に記載した玉軸受。2. A cage made of steel for holding a plurality of balls is provided, and by subjecting this cage to nitriding treatment, at least the rolling of each of the balls on the surface of the cage during operation is performed. The ball bearing according to claim 1, wherein a nitriding layer having a thickness of 3 to 20 µm is formed in a portion that is in sliding contact with the moving surface.
してグリースを使用する、請求項1〜2の何れかに記載
した玉軸受。3. The ball bearing according to claim 1, wherein grease is used as a lubricant for lubricating the installation portion of the plurality of balls.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002115666A JP2003314561A (en) | 2002-04-18 | 2002-04-18 | Ball bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002115666A JP2003314561A (en) | 2002-04-18 | 2002-04-18 | Ball bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2003314561A true JP2003314561A (en) | 2003-11-06 |
Family
ID=29533755
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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JP2002115666A Pending JP2003314561A (en) | 2002-04-18 | 2002-04-18 | Ball bearing |
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005282752A (en) * | 2004-03-30 | 2005-10-13 | Koyo Seiko Co Ltd | Rolling bearing |
JP2006017218A (en) * | 2004-07-01 | 2006-01-19 | Nissan Motor Co Ltd | Sliding device |
JP2009202307A (en) * | 2008-02-28 | 2009-09-10 | Nsk Ltd | Grinding method for rolling and sliding device member and rolling and sliding device member |
CN102527899A (en) * | 2010-11-30 | 2012-07-04 | 株式会社神户制钢所 | Mold for plastic forming and a method for producing the same, and method for forging aluminum material |
WO2014077077A1 (en) | 2012-11-16 | 2014-05-22 | Ntn株式会社 | Crown-shaped retainer |
JP2015215061A (en) * | 2014-05-12 | 2015-12-03 | 日本精工株式会社 | Rolling bearing |
IT201900000238A1 (en) * | 2019-01-09 | 2020-07-09 | Skf Ab | ROLLING CONTACT BEARING WITH IMPROVED PERFORMANCES |
-
2002
- 2002-04-18 JP JP2002115666A patent/JP2003314561A/en active Pending
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005282752A (en) * | 2004-03-30 | 2005-10-13 | Koyo Seiko Co Ltd | Rolling bearing |
JP2006017218A (en) * | 2004-07-01 | 2006-01-19 | Nissan Motor Co Ltd | Sliding device |
JP2009202307A (en) * | 2008-02-28 | 2009-09-10 | Nsk Ltd | Grinding method for rolling and sliding device member and rolling and sliding device member |
CN102527899A (en) * | 2010-11-30 | 2012-07-04 | 株式会社神户制钢所 | Mold for plastic forming and a method for producing the same, and method for forging aluminum material |
CN102527899B (en) * | 2010-11-30 | 2014-08-06 | 株式会社神户制钢所 | Mold for plastic forming and a method for producing the same, and method for forging aluminum material |
US8822027B2 (en) | 2010-11-30 | 2014-09-02 | Kobe Steel, Ltd. | Mold for plastic forming and a method for producing the same, and method for forging aluminum material |
WO2014077077A1 (en) | 2012-11-16 | 2014-05-22 | Ntn株式会社 | Crown-shaped retainer |
US9546681B2 (en) | 2012-11-16 | 2017-01-17 | Ntn Corporation | Crown shaped retainer |
JP2015215061A (en) * | 2014-05-12 | 2015-12-03 | 日本精工株式会社 | Rolling bearing |
IT201900000238A1 (en) * | 2019-01-09 | 2020-07-09 | Skf Ab | ROLLING CONTACT BEARING WITH IMPROVED PERFORMANCES |
US11078960B2 (en) | 2019-01-09 | 2021-08-03 | Aktiebolaget Skf | Rolling contact bearing with improved performances |
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