JP2003301851A - Solid lubricating roller bearing - Google Patents

Solid lubricating roller bearing

Info

Publication number
JP2003301851A
JP2003301851A JP2002109548A JP2002109548A JP2003301851A JP 2003301851 A JP2003301851 A JP 2003301851A JP 2002109548 A JP2002109548 A JP 2002109548A JP 2002109548 A JP2002109548 A JP 2002109548A JP 2003301851 A JP2003301851 A JP 2003301851A
Authority
JP
Japan
Prior art keywords
bearing
spacer
life
rollers
roller
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
Application number
JP2002109548A
Other languages
Japanese (ja)
Other versions
JP3981814B2 (en
Inventor
Kenji Sunahara
賢治 砂原
Mitsuaki Ikeda
満昭 池田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yaskawa Electric Corp
Original Assignee
Yaskawa Electric Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Yaskawa Electric Corp filed Critical Yaskawa Electric Corp
Priority to JP2002109548A priority Critical patent/JP3981814B2/en
Publication of JP2003301851A publication Critical patent/JP2003301851A/en
Application granted granted Critical
Publication of JP3981814B2 publication Critical patent/JP3981814B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F16C33/37—Loose spacing bodies
    • F16C33/3706—Loose spacing bodies with concave surfaces conforming to the shape of the rolling elements, e.g. the spacing bodies are in sliding contact with the rolling elements
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6696—Special parts or details in view of lubrication with solids as lubricant, e.g. dry coatings, powder

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a solid lubricating roller bearing being free of early lock and roller skewing due to the biting of wear powder and having smaller bearing torque, a larger loading capacity and a longer life. <P>SOLUTION: The solid lubricating roller bearing comprises an inner ring 1 and an outer ring 2, an inner ring rolling groove 3 and an outer ring rolling groove 4 provided on each surface opposed to the inner ring 1 and outer ring 2, respectively, and a plurality of rollers 5 inserted between the two rolling grooves 3, 4. Solid lubricant coatings are applied to all or part of the surfaces of these structural components and spacers are mounted and held between the rollers 5. The plurality of spherical or cylindrical spacers 6 have diameters being 20-48% of diameters of the rollers 5 and are mounted between the pair of rollers 5. There are less wear powder and no early lock of the bearing while preventing skewing. <P>COPYRIGHT: (C)2004,JPO

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】本発明は、真空中、高温、低
温あるいは放射線下などの過酷な環境下で使用される固
体潤滑ころ軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a solid lubricated roller bearing used in a harsh environment such as vacuum, high temperature, low temperature or radiation.

【０００２】[0002]

【従来の技術】従来、真空中、高温、低温あるいは放射
線下などの過酷な環境下で使用される固体潤滑ころ軸受
は、図７〜図１０のようになっている。2. Description of the Related Art Conventionally, solid lubricating roller bearings which are used in a harsh environment such as vacuum, high temperature, low temperature or radiation are as shown in FIGS.

【０００３】図７は第１の従来例を示すクロスローラ軸
受であって、（ａ）はその一部を示す平面図、（ｂ）は
スペーサの斜視図、図８はクロスローラ軸受の側面展開
図である。図７、８において、１１は内輪、１２は外
輪、１５はころ、１６はスペーサである。図に示すよう
に転走溝の形状を周方向にのびるＶ形にし、隣同士のこ
ろを９０度向きを変えてクロスさせた、ころ軸受の一種
であるクロスローラ軸受において、ころ１５の表面に固
体潤滑剤を被覆し、スペーサ１６の形状をその左右両側
面に互いに隣接するころ１５が回転可能に嵌合する曲面
溝１６ａにしたものが提案されている（特開平１０−１
４１３６３号公報）。クロスローラ軸受は、モーメント
が負荷できる特徴があるため、ロボットのアーム端部な
どに使われる軸受で、アームのガタを無くすため、一般
的に軸受の内部隙間を５ミクロン以下と非常に小さく設
定して使われる。FIG. 7 is a cross roller bearing showing a first conventional example, (a) is a plan view showing a part thereof, (b) is a perspective view of a spacer, and FIG. 8 is a side surface development of the cross roller bearing. It is a figure. In FIGS. 7 and 8, 11 is an inner ring, 12 is an outer ring, 15 is a roller, and 16 is a spacer. As shown in the figure, in the cross roller bearing which is a kind of roller bearing in which the rolling groove has a V shape extending in the circumferential direction and adjacent rollers are crossed by changing the direction by 90 degrees, the surface of the roller 15 is It is proposed that the spacer 16 is coated with a solid lubricant, and the spacer 16 has a curved groove 16a on both left and right side surfaces of which the rollers 15 adjacent to each other are rotatably fitted (Japanese Patent Laid-Open No. 10-1).
No. 41363). Since the cross roller bearing has a characteristic of being able to apply a moment, it is a bearing used at the end of the arm of a robot, etc. Generally, the inner clearance of the bearing is set to a very small value of 5 microns or less in order to eliminate rattling of the arm. Used.

【０００４】図９は第２の従来例を示すクロスローラ軸
受の側面展開図である。図９において、２１は内輪、２
２は外輪、２５はころ、２６、２７はスペーサである。
第２の従来例では、クロスローラ軸受において、ころ２
５の表面に固体潤滑剤を被覆せず、円柱状や球状のスペ
ーサ２６、２７を設けたものが提案されている（実開平
２−７４６２５号公報）。FIG. 9 is a side development view of a cross roller bearing showing a second conventional example. In FIG. 9, 21 is an inner ring, 2
2 is an outer ring, 25 is a roller, and 26 and 27 are spacers.
In the second conventional example, in the cross roller bearing, the roller 2
It has been proposed that the surface of No. 5 is not coated with a solid lubricant and is provided with columnar or spherical spacers 26 and 27 (Japanese Utility Model Laid-Open No. 2-74625).

【０００５】また、第１、第２の従来例のころ軸受に替
えて玉軸受の例を第１の比較例として図１０に示す。図
１０は第１の比較例を示す玉軸受の正断面図である。第
１、第２の従来例に示したころ軸受に替えて玉軸受とし
たもので、玉３５の表面に固体潤滑剤３７を被覆し、ス
ペーサ３６の形状を球状にしたものが提案されている
（実開昭５９−９２２１９号公報）。FIG. 10 shows a ball bearing example as a first comparative example in place of the roller bearings of the first and second conventional examples. FIG. 10 is a front sectional view of a ball bearing showing a first comparative example. It has been proposed to replace the roller bearings shown in the first and second conventional examples with ball bearings, in which the surface of the balls 35 is coated with a solid lubricant 37 and the spacers 36 have a spherical shape. (Japanese Utility Model Publication No. 59-92219).

【０００６】[0006]

【発明が解決しようとする課題】ところが、第１の従来
例では、スペーサの形状がころにフィットする接触面積
が広い曲面溝であるため、ころの回転に伴うころとスペ
ーサの摺動で、スペーサの材料成分が摩耗粉として多く
発生し、軸受内部に堆積するために軸受の内部隙間にか
みこみ、軸受が早期にロックするという問題を起こす。However, in the first prior art example, since the shape of the spacer is a curved groove having a wide contact area for fitting the roller, the spacer slides due to the sliding of the roller and the spacer as the roller rotates. A large amount of the material component of is generated as wear powder, and it is deposited inside the bearing, so that it bites into the inner clearance of the bearing, causing a problem of early locking of the bearing.

【０００７】また、第２の従来例では、スペーサをころ
間毎に１個配置し、そのスペーサの形状を円柱状や球状
にし、ころにフィットしないようにしているため、摩耗
粉は多くなく、軸受が早期にロックする問題は生じない
が、 ころの表面に固体潤滑剤が無いため、ころと内・外輪
の摩擦抵抗が大きく、軸受トルクが大きいとか、軸受寿
命が短いという問題を起こす。スペーサがころにフィ
ットしないため、ころのスキュー（揺れ）が起こり、滑
り成分が増え、軸受寿命が短いという問題を起こす。
スペーサの占有容積が大きいため、ころの数が減り負荷
容量が小さくなり寿命が短くなる。Further, in the second conventional example, one spacer is arranged for each roller, and the shape of the spacer is cylindrical or spherical so as not to fit the rollers. The problem of the bearing locking early does not occur, but since there is no solid lubricant on the surface of the roller, frictional resistance between the roller and the inner and outer rings is large, bearing torque is large, and bearing life is short. Since the spacers do not fit the rollers, roller skew (sway) occurs, sliding components increase, and the bearing life is shortened.
Since the space occupied by the spacer is large, the number of rollers is reduced, the load capacity is reduced, and the life is shortened.

【０００８】また、第１の比較例では、玉の表面に固体
潤滑剤を被覆することで、第２の従来例の弱点を補って
いるが、もともと玉軸受では接触が点接触であるため、
接触ポイント以外で摩耗粉をよけることが出来、ロック
防止に関して改善効果は無い。むしろ、玉軸受の場合
は、球状のスペーサより、占有容積を小さくできる王冠
形保持器で玉同士の接触を防ぐ方が寿命が長い。そこで
本発明は、摩耗粉のかみこみによる早期ロックやころの
スキューが発生せず、軸受トルクが小さく、負荷容量が
大きい、長寿命な固体潤滑ころ軸受を提供することを目
的とする。Further, in the first comparative example, the weakness of the second conventional example is compensated by coating the surface of the ball with a solid lubricant, but since the ball bearing is originally a point contact,
Abrasion powder can be avoided at points other than the contact point, and there is no improvement effect in terms of lock prevention. Rather, in the case of a ball bearing, it is longer in service life to prevent the balls from contacting with each other by using a crown-shaped cage that can occupy less space than a spherical spacer. Therefore, an object of the present invention is to provide a long-life solid-lubricated roller bearing that does not cause early locking or roller skew due to wear dust entrainment, has a small bearing torque, and has a large load capacity.

【０００９】[0009]

【課題を解決するための手段】上記問題を解決するた
め、本発明は、以下のようにするものである。請求項１
の本発明は、内輪と外輪と、前記内輪と前記外輪のそれ
ぞれ対向する面に設けた内輪転走溝と外輪転走溝と、前
記二つの転走溝の間に挿入した複数個のころを備え、こ
れら構成部品の表面の一部または全部に固体潤滑剤の被
膜を形成し、前記ころ間に介装させて保持するスペーサ
とからなる固体潤滑ころ軸受において、前記スペーサを
球状または円柱状で構成したものである。上記手段によ
り、摩耗粉の発生が減り、摩耗粉かみこみによる早期ロ
ックが無くなる。In order to solve the above problems, the present invention is as follows. Claim 1
The present invention, an inner ring and an outer ring, an inner ring rolling groove and an outer ring rolling groove provided on the respective surfaces of the inner ring and the outer ring facing each other, a plurality of rollers inserted between the two rolling grooves. In a solid lubricating roller bearing comprising a spacer that holds a solid lubricant coating on a part or all of the surfaces of these constituent parts and is interposed between the rollers, the spacer is spherical or cylindrical. It is composed. By the above-mentioned means, the generation of wear debris is reduced, and the premature locking due to wear debris is eliminated.

【００１０】請求項２の本発明は、請求項１記載の固体
潤滑ころ軸受において、前記スペーサの直径が前記ころ
の直径の２０％〜４８％であり、一対のころ間に介装さ
せる前記スペーサの個数を複数としたものである。上記
手段により、スキューを防止しつつ、摩耗粉の発生を減
らし、軸受の早期ロックを無くすことができる。According to a second aspect of the present invention, in the solid lubricating roller bearing according to the first aspect, the diameter of the spacer is 20% to 48% of the diameter of the roller, and the spacer is interposed between the pair of rollers. The number of is a plurality. By the above means, it is possible to prevent the skew, reduce the generation of abrasion powder, and eliminate the early locking of the bearing.

【００１１】請求項３の本発明は、請求項１または２記
載の固体潤滑ころ軸受において、前記スペーサの表面に
二硫化モリブデンを被覆したものである。上記手段によ
り、スペーサの表面の二硫化モリブデンが潤滑剤の供給
源となり軸受の寿命が延びる。なお、二硫化モリブデン
は薄膜として被覆しているので、摩耗粉も粒径が小さ
く、かみ込みによる軸受ロックは起こらない。According to a third aspect of the present invention, in the solid lubricating roller bearing according to the first or second aspect, the surface of the spacer is coated with molybdenum disulfide. By the above means, molybdenum disulfide on the surface of the spacer serves as a lubricant supply source to extend the life of the bearing. In addition, since molybdenum disulfide is coated as a thin film, the wear powder also has a small particle size, and bearing lock due to biting does not occur.

【００１２】請求項４の本発明は、請求項３記載の固体
潤滑ころ軸受において、前記スペーサの表面に被覆した
二硫化モリブデンの膜中に酸素、窒素、炭素、またはホ
ウ素のいずれかの元素を含むこものである。上記手段に
より、二硫化モリブデンの膜が剥がれ易くなり、供給源
として効果が大きくなり、軸受の寿命がさらに延びる。According to a fourth aspect of the present invention, in the solid lubricated roller bearing according to the third aspect, any element of oxygen, nitrogen, carbon, or boron is contained in the molybdenum disulfide film coated on the surface of the spacer. It is included. By the above means, the molybdenum disulfide film is easily peeled off, the effect as a supply source is increased, and the life of the bearing is further extended.

【００１３】請求項５の本発明は、請求項１または２記
載の固体潤滑ころ軸受において、前記スペーサは二硫化
モリブデンを含有した樹脂材料からなるものである。上
記手段により、これらの潤滑成分が長期にわたり、潤滑
供給源として働き、軸受の寿命が延びる。According to a fifth aspect of the present invention, in the solid lubricating roller bearing according to the first or second aspect, the spacer is made of a resin material containing molybdenum disulfide. By the above means, these lubricating components serve as a lubrication supply source for a long period of time, and the life of the bearing is extended.

【００１４】[0014]

【発明の実施の形態】以下、本発明の実施例を図に基づ
いて説明する。 （第１の実施例）図１は本発明の第１の実施例〜第３の
実施例に共通なクロスローラ軸受の側面展開図で、外輪
を一部切り欠いている。また、図２は第１図のＡ−Ａ線
に沿う拡大断面図である。１は内輪、２は２つ割りにし
た外輪、３は内輪の外周面に設けたＶ形の内輪転走溝、
４は外輪２の内周面に内輪転走溝３に対向して設けた同
形の外輪転走溝である。５は前記転走溝３、４間に配置
されたＳＵＳ４４０Ｃ製のころで、交互に方向を変えて
配置してある。第１の実施例の特徴は、ころ５の表面に
は固体潤滑剤である二硫化モリブデンを１μｍ被覆し、
ころ５同士の間に球状のスペーサ６をそれぞれ挿入配置
した点である、ここで、スペーサ６の直径はころ５の直
径よりを３０μｍ小さくしている。このような構成で、
内輪１と外輪２が相対的に回転すると、ころ５が自転し
ながら、内輪転送溝３および外輪転走溝４内で移動し、
内輪１と外輪２の相対運動を支持する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) FIG. 1 is a side development view of a cross roller bearing common to the first to third embodiments of the present invention, in which an outer ring is partially cut away. 2 is an enlarged sectional view taken along the line AA of FIG. 1 is an inner ring, 2 is an outer ring divided into two, 3 is a V-shaped inner ring rolling groove provided on the outer peripheral surface of the inner ring,
Reference numeral 4 denotes an outer race rolling groove of the same shape provided on the inner peripheral surface of the outer race 2 so as to face the inner race rolling groove 3. Reference numeral 5 is a roller made of SUS440C arranged between the rolling grooves 3 and 4 and arranged by alternately changing the direction. The characteristic of the first embodiment is that the surface of the roller 5 is coated with 1 μm of molybdenum disulfide, which is a solid lubricant,
This is the point where spherical spacers 6 are inserted and arranged between the rollers 5, respectively. Here, the diameter of the spacers 6 is smaller than the diameter of the rollers 5 by 30 μm. With such a configuration,
When the inner ring 1 and the outer ring 2 rotate relatively, the rollers 5 rotate in the inner ring transfer groove 3 and the outer ring rolling groove 4 while rotating,
It supports the relative movement of the inner ring 1 and the outer ring 2.

【００１５】次に、第１の実施例の効果を確認する上で
行った試験結果を説明する。本実施例では、スペーサの
材料として、（１）自己潤滑性樹脂（本実施例ではＰＥ
ＥＫ＋ＰＴＦＥの複合樹脂）と、（２）ＳＵＳ４４０Ｃ
の２種類を用意し、軸受を構成した。そして、軸受寿命
の評価には、軸受２個に、２１５Ｎのアキシャル荷重を
負荷して、３２０ｒ／ｍｉｎで回転させる寿命試験機を
用い、内径３０ｍｍ、外径５５ｍｍ、幅１０ｍｍの軸受
を評価した。試験中にはモータのトルク出力をモニタ
し、定常時のトルクの２倍を越えた時点を軸受寿命とし
た。なお、以下に示す各実施例、従来例および比較例の
軸受寿命については、第１の従来例における軸受寿命実
測値に対する比率（寿命比）として表した（すなわち、
第１の従来例の寿命比は１となる）。 表１に試験結果として定常時のトルクと軸受寿命比を示
す。Next, the test results conducted to confirm the effect of the first embodiment will be described. In this embodiment, the material of the spacer is (1) self-lubricating resin (PE in this embodiment).
EK + PTFE composite resin) and (2) SUS440C
The bearing was constructed by preparing two types of. To evaluate the bearing life, a bearing tester having an inner diameter of 30 mm, an outer diameter of 55 mm and a width of 10 mm was evaluated using a life tester in which two bearings were loaded with an axial load of 215 N and rotated at 320 r / min. During the test, the torque output of the motor was monitored, and the point in time when the torque exceeded twice the steady state torque was taken as the bearing life. The bearing life of each of the following examples, conventional examples and comparative examples is expressed as a ratio (life ratio) to the actual measured value of the bearing life in the first conventional example (that is,
The life ratio of the first conventional example is 1.) Table 1 shows the steady-state torque and bearing life ratio as test results.

【００１６】[0016]

【表１】 [Table 1]

【００１７】併せて表１に、第１の従来例としてスペー
サを、その左右両側面に互いに隣接するころが回転可能
に嵌合する曲面溝にしたもので構成した軸受の軸受寿命
の結果を示す。また、第２の従来例として第１の実施例
（１）から転動体表面の潤滑膜を除いた構成の軸受を寿
命試験した結果を示す。さらに、本発明の効果が玉軸受
と比べころ軸受が顕著であることを示すため、第１の比
較例として転動体を玉とし、第１の比較例（１）ではス
ペーサをＳＵＳ４４０Ｃの球状とした軸受、第１の比較
例（２）では自己潤滑性樹脂の曲面溝を持つ王冠型保持
器を備えた軸受を寿命試験した結果を示す。なお、玉軸
受の寿命試験では上述のクロスローラ軸受と規格上近い
内径３０ｍｍ、外径５５ｍｍ、幅１３ｍｍの軸受を用
い、評価した。なお、第１の比較例（１）の軸受は転動
体の数が９個であるのに対し、第１の比較例（２）では
曲面溝を持つ王冠型保持器の占有容積が球状スペーサよ
り小さいため、転動体の数を多くでき、１２個の転動体
を備えている。In addition, Table 1 shows the results of the bearing life of a bearing as a first conventional example, in which a spacer is formed with curved grooves on both left and right side surfaces of which adjacent rollers are rotatably fitted. . Further, as a second conventional example, the result of a life test of a bearing having a configuration in which the lubricating film on the surface of the rolling element is removed from the first embodiment (1) is shown. Further, since the effect of the present invention is more remarkable in the roller bearing than in the ball bearing, the rolling element is a ball as the first comparative example, and the spacer is a SUS440C spherical shape in the first comparative example (1). In the first comparative example (2), the results of the life test of bearings having a crown type cage having curved grooves of self-lubricating resin are shown. In addition, in the life test of the ball bearing, a bearing having an inner diameter of 30 mm, an outer diameter of 55 mm, and a width of 13 mm, which is close to the standard in the cross roller bearing, was used for evaluation. In the bearing of the first comparative example (1), the number of rolling elements is 9, whereas in the first comparative example (2), the crown cage having the curved groove occupies more space than the spherical spacer. Since it is small, the number of rolling elements can be increased, and twelve rolling elements are provided.

【００１８】軸受寿命については、第1の実施例（１）
の寿命比が７．２であり、第1の実施例（２）で５．１
であるため、第１の従来例より延長効果が認められた。
試験後に、第１の実施例の軸受を分解すると、ころと摺
動するスペーサの曲面溝部分に、摩耗粉が堆積している
ことが観察された。一方、第1の実施例（１）、（２）
の軸受のいずれも摩耗粉は認められなかった。これは、
第１の実施例の軸受で発生した摩耗粉が、軸受の早期ロ
ックの原因になっている事の裏付けである。次に、第１
の実施例（１）と比較し、転動体表面の潤滑膜が無い第
２の従来例を取り上げ、第１の実施例（１）の効果を説
明する。第２の従来例では定常時のトルクが１．３×１
０-1Ｎ・ｍであり、第１の実施例（１）の３．９×１０
-2Ｎ・ｍと比べ、一桁トルクが大きい。また、第２の従
来例の軸受寿命比が０．６であるため、第１の実施例
（１）の軸受寿命比７．２と比べると、一桁軸受寿命が
短かった。転動体表面の潤滑膜が無いため、ころと内・
外輪の摩擦抵抗が大きく、軸受トルクが大きくなったも
のである。そのため、軸受寿命が短くなったものであ
る。次に、第１の実施例（２）、第１の従来例、第１の
比較例（１）、（２）を取り上げ、ころ軸受と玉軸受で
本発明の効果の差異を説明する。まず、ころ軸受の第１
の実施例（２）と第１の従来例を比較すると、ＳＵＳ４
４０Ｃの球状のスペーサを有する第１の実施例（２）が
軸受寿命比５．１であるため、自己潤滑製樹脂の曲面溝
のスペーサを有する第１の従来例より長寿命であり、ス
ペーサを球状にした効果が認められた。一方、第１の実
施例（２）を玉軸受の第１の比較例（１）および（２）
と比較すると、ＳＵＳ４４０Ｃの球状のスペーサを有す
る第１の比較例（１）の軸受寿命比が６．５であり、自
己潤滑製樹脂の曲面溝のスペーサを有する第１の比較例
（２）の軸受寿命比が２６．５であるため、、第１の実
施例（２）はこれらの比較例より短寿命で、スペーサを
球状にした効果は認められないどころか、逆効果が現れ
た。このように、第１の実施例は、線接触するころ軸受
では摩耗粉がかみ込み軸受ロックに至るという現象に着
目し、スペーサの形状をころとフィットしないように球
状としたので、摩耗粉の発生を押さられ、ころで問題と
なる磨耗紛のかみこみによる軸受の早期ロックを防止す
ることができる。一方、玉軸受では接触が点接触である
ため、接触ポイント以外で摩耗粉をよけることが出来、
ロック防止に関して改善効果が得られない。むしろ、玉
軸受の場合は、球状のスペーサより、曲面溝を持つ王冠
型保持器の方が占有容積を小さくでき、球数を増やせる
ので、耐荷重性が増し、寿命延長効果が大きい。また、
ころの表面に固体潤滑剤を被覆しているので、ころと内
・外輪の摩擦抵抗が小さくなり、軸受トルクが小さい
上、軸受寿命が長くなるという効果がある。Regarding the bearing life, the first embodiment (1)
Has a life ratio of 7.2, which is 5.1 in the first embodiment (2).
Therefore, the extension effect was recognized as compared with the first conventional example.
After the test, when the bearing of the first embodiment was disassembled, it was observed that abrasion powder was deposited on the curved surface groove portion of the spacer sliding with the roller. On the other hand, the first embodiment (1), (2)
No wear debris was found on any of the bearings. this is,
This is a proof that the abrasion powder generated in the bearing of the first embodiment causes the early locking of the bearing. Then the first
The effect of the first embodiment (1) will be described by taking the second conventional example in which there is no lubricating film on the surface of the rolling element as compared with the embodiment (1). In the second conventional example, the steady-state torque is 1.3 × 1.
0 −1 N · m, which is 3.9 × 10 of the first embodiment (1).
Compared to -2 N ・ m, the torque is one digit higher. Further, since the bearing life ratio of the second conventional example is 0.6, the one-digit bearing life was shorter than the bearing life ratio of 7.2 of the first embodiment (1). Since there is no lubricating film on the rolling element surface,
The friction resistance of the outer ring is large and the bearing torque is large. Therefore, the bearing life is shortened. Next, the difference in the effect of the present invention between the roller bearing and the ball bearing will be described by taking the first embodiment (2), the first conventional example, and the first comparative examples (1) and (2). First, the first roller bearing
Comparing the embodiment (2) with the first conventional example, SUS4
Since the first embodiment (2) having the spherical spacer of 40C has a bearing life ratio of 5.1, it has a longer life than the first conventional example having the spacer of the curved groove of the self-lubricating resin. A spherical effect was recognized. On the other hand, the first embodiment (2) is the first comparative example (1) and (2) of the ball bearing.
Comparing with, the bearing life ratio of the first comparative example (1) having the spherical spacer of SUS440C is 6.5, and the bearing life ratio of the first comparative example (2) having the curved groove spacer of the self-lubricating resin. Since the bearing life ratio was 26.5, the first embodiment (2) had a shorter life than these comparative examples, and the effect of making the spacer spherical was not recognized, but the opposite effect appeared. As described above, in the first embodiment, attention is paid to the phenomenon that wear powder reaches the bearing lock by biting in the roller bearing in line contact, and the shape of the spacer is made spherical so as not to fit with the rollers. It is possible to prevent the bearing from being prematurely locked due to the generation of abrasion powder, which is a problem with the rollers. On the other hand, in ball bearings, the contact is point contact, so it is possible to avoid abrasion powder at points other than the contact point,
No improvement effect can be obtained for lock prevention. Rather, in the case of a ball bearing, a crown type cage having a curved groove can occupy a smaller volume and can increase the number of balls than a spherical spacer, so that the load bearing property is increased and the life extension effect is great. Also,
Since the surface of the roller is coated with the solid lubricant, the frictional resistance between the roller and the inner / outer rings is reduced, the bearing torque is small, and the bearing life is extended.

【００１９】次に、本発明の第２の実施例について説明
する。第２の実施例では、第１の実施例（２）に加え、
スペーサ６表面に二硫化モリブデンを１μｍの膜厚で被
覆したものである。軸受寿命を評価した結果を表２に示
す。Next, a second embodiment of the present invention will be described. In the second embodiment, in addition to the first embodiment (2),
The surface of the spacer 6 is coated with molybdenum disulfide to a film thickness of 1 μm. Table 2 shows the results of evaluation of the bearing life.

【００２０】[0020]

【表２】 [Table 2]

【００２１】第２の実施例の軸受寿命比は８であり、ス
ペーサ６表面に二硫化モリブデンを被覆していない第１
の実施例（２）の寿命比５．１と比較すると、寿命延長
の効果が認められた。このように、第２の実施例は、ス
ペーサ６表面の二硫化モリブデンが潤滑剤の供給源とな
るため、軸受寿命を延長することができる。二硫化モリ
ブデンを１μｍの薄膜として被覆しているため、剥がれ
た二硫化モリブデンの摩耗粉の粒径（サイズ）も十分小
さく、軸受の内部隙間にかみ込んでロックするという副
作用も防止することができる。The bearing life ratio of the second embodiment is 8, and the surface of the spacer 6 is not coated with molybdenum disulfide.
When compared with the life ratio of 5.1 in Example (2), the effect of extending the life was recognized. As described above, in the second embodiment, since the molybdenum disulfide on the surface of the spacer 6 serves as the lubricant supply source, the bearing life can be extended. Since molybdenum disulfide is coated as a thin film with a thickness of 1 μm, the particle size (size) of the abrasion powder of the molybdenum disulfide that has been peeled off is sufficiently small, and the side effect of being locked by being caught in the inner clearance of the bearing can be prevented. .

【００２２】次に、本発明の第３の実施例について説明
する。第３の実施例では、第２の実施例でスペーサの表
面に被覆した二硫化モリブデンの膜中に酸素を１０％添
加したものである。軸受寿命を評価した結果を表２に併
せて示す。第３の実施例では軸受寿命比が１９．５であ
り、酸素を添加していない第２の実施例の寿命比８と比
較すると、寿命延長の効果が顕著に認められた。このよ
うに、第３の実施例は膜中に酸素を添加すると、膜が剥
がれ易くなると共に、供給源としての効果が大きくな
り、軸受寿命を延長することができる。Next, a third embodiment of the present invention will be described. In the third embodiment, 10% of oxygen is added to the film of molybdenum disulfide coated on the surface of the spacer in the second embodiment. The results of evaluating the bearing life are also shown in Table 2. In the third embodiment, the bearing life ratio was 19.5, and when compared with the life ratio 8 of the second embodiment in which oxygen was not added, the effect of extending the life was remarkably recognized. As described above, in the third embodiment, when oxygen is added to the film, the film is easily peeled off, the effect as a supply source is increased, and the life of the bearing can be extended.

【００２３】次に、本発明の第４の実施例を説明する。
図３は本発明の第４〜第８の実施例に共通なクロスロー
ラ軸受の側面展開図で、外輪を一部切り欠いている。ま
た、図４は図３のＡ−Ａ線に沿う拡大断面図である。図
において、５は転走溝３、４間に配置されたＳＵＳ４４
０Ｃ製のころで、交互に方向を変えて配置してある。第
４の実施例の特徴は、ころ５の表面には固体潤滑剤であ
る二硫化モリブデンを１μｍ被覆し、隣り合うころ５同
士の間に球状の４個のスペーサ６をそれぞれ挿入配置し
た点である。なお、スペーサ６の直径はころ５の直径の
３０％にしている。Next, a fourth embodiment of the present invention will be described.
FIG. 3 is a side development view of a cross roller bearing common to the fourth to eighth embodiments of the present invention, in which an outer ring is partially cut away. 4 is an enlarged sectional view taken along the line AA of FIG. In the figure, 5 is a SUS44 arranged between the rolling grooves 3 and 4.
It is a roller made of 0C, and the direction is alternately changed. The feature of the fourth embodiment is that the surface of the roller 5 is coated with 1 μm of molybdenum disulfide, which is a solid lubricant, and four spherical spacers 6 are inserted and arranged between adjacent rollers 5. is there. The diameter of the spacer 6 is 30% of the diameter of the roller 5.

【００２４】軸受の組立の手順を以下に示す。２つ割り
の外輪２の１つを平板上に寝かせて置き、その内側に内
輪１を寝かせて置く。外輪２と内輪１の間にころ５を所
定の個数、配置する。その際、隣り合うころ５同士の方
向を変えて配置する。ころ５同士の間にスペーサ６を配
置する。その際、１組のころ５間に４個のスペーサ６を
配置する。この手順で軸受を組み立てるが、スペーサ６
の直径がころ５の直径の２０％未満だと、スペーサ６を
配置する際、スペーサ６がばらけてしまい、組立が困難
になる。また、５０％以上だと物理的に配置できない。
この理由で、スペーサ６の直径はがころ５の直径の２０
〜４８％程度と決まる。このように、第４の実施例は第
１〜第３の実施例と同様にころ５同士間に球状のスペー
サ６を配置しているので、ころ５とスペーサ６がフィッ
トせず、スペーサ６からの摩耗粉が過大に発生しない。
また、スペーサ６を図３、４の様にころ５の形状に沿う
形に４個配置しているので、ころ５のスキューが生じな
い。さらにスペーサ６の占有容積が小さいので、ころ５
の数を増やし、負荷容量を増やすことができる。なお、
１組のころ５間に配置するスペーサ６の数は２個の場合
でも、同じ機能を果たす。The procedure for assembling the bearing will be described below. One of the two outer rings 2 is laid on a flat plate, and the inner ring 1 is laid on the inside. A predetermined number of rollers 5 are arranged between the outer ring 2 and the inner ring 1. At this time, the adjacent rollers 5 are arranged with their directions changed. A spacer 6 is arranged between the rollers 5. At that time, four spacers 6 are arranged between the pair of rollers 5. Assemble the bearing in this procedure, but use the spacer 6
If the diameter is less than 20% of the diameter of the roller 5, the spacers 6 will be separated when the spacers 6 are arranged, and assembling will be difficult. Further, if it is 50% or more, it cannot be physically arranged.
For this reason, the diameter of the spacer 6 is 20 times that of the roller 5.
It is decided to be about 48%. As described above, in the fourth embodiment, since the spherical spacer 6 is arranged between the rollers 5 as in the first to third embodiments, the rollers 5 and the spacer 6 do not fit, and No excessive abrasion powder is generated.
Further, since four spacers 6 are arranged along the shape of the roller 5 as shown in FIGS. 3 and 4, skew of the roller 5 does not occur. Furthermore, since the space occupied by the spacer 6 is small, the roller 5
The load capacity can be increased by increasing the number of. In addition,
Even when the number of spacers 6 arranged between one pair of rollers 5 is two, the same function is achieved.

【００２５】次に、本発明の第５の実施例を説明する。
第５の実施例では、スペーサ６としてＳＵＳ４４０Ｃの
軸受ボールで軸受を構成した。そして、軸受寿命の評価
には、軸受２個に、２１５Ｎのアキシャル荷重を負荷し
て、３２０ｒ／ｍｉｎで回転させる寿命試験機を用い、
内径３０ｍｍ、外径５５ｍｍ、幅１０ｍｍの軸受を評価
した。試験中にはモータのトルク出力をモニタし、定常
時のトルクの２倍を越えた時点を軸受寿命とした。表３
に試験結果として定常時のトルクと軸受寿命比を示す。Next, a fifth embodiment of the present invention will be described.
In the fifth embodiment, the bearing is made of SUS440C bearing balls as the spacer 6. Then, for the evaluation of the bearing life, a life tester in which two bearings are loaded with an axial load of 215 N and rotated at 320 r / min,
A bearing having an inner diameter of 30 mm, an outer diameter of 55 mm and a width of 10 mm was evaluated. During the test, the torque output of the motor was monitored, and the point in time when the torque exceeded twice the steady state torque was taken as the bearing life. Table 3
The torque and the bearing life ratio at steady state are shown in the test results.

【００２６】[0026]

【表３】 [Table 3]

【００２７】併せて表３に、第１の従来例としてスペー
サを、その左右両側面に互いに隣接するころが回転可能
に嵌合する曲面溝にしたもので構成した軸受の軸受寿命
の結果を示す。また、第２の従来例としてスペーサを１
組のころ間に１個配置した構成の軸受を寿命試験した結
果を示す。なお、第５の実施例、第１の従来例ではころ
の数が２４個であるのに対し、第２の従来例の軸受はス
ペーサの占有容積が大きいため、ころの数が１８個とな
っている。In addition, Table 3 shows the results of the bearing life of the bearing as a first conventional example, in which the spacer is formed with curved grooves on both left and right side surfaces of which adjacent rollers are rotatably fitted. . As a second conventional example, one spacer is used.
The results of the life test of a bearing having a structure in which one roller is arranged between the rollers are shown. In the fifth embodiment and the first conventional example, the number of rollers is 24, whereas in the bearing of the second conventional example, the space occupied by the spacer is large, so the number of rollers is 18. ing.

【００２８】第５の実施例の軸受寿命比は９．２であ
り、第１の従来例と比較すると延長効果が認められた。
試験後に、第５の実施例の軸受を分解すると、ころと摺
動するスペーサの曲面溝部分に、摩耗粉が堆積している
ことが観察された。一方、第５の実施例の軸受では摩耗
粉は認められなかった。これは、第５の実施例の軸受で
発生した摩耗粉が、軸受の早期ロックの原因になってい
る事の裏付けである。また、第５の実施例の軸受寿命比
は９．２であり、第２の従来例の軸受寿命比５．１と比
較しても寿命が長く、ころの個数が増えていることと、
ころのスキューを防止できたことで寿命が延長したもの
である。The bearing life ratio of the fifth embodiment was 9.2, and an extension effect was recognized as compared with the first conventional example.
After the test, when the bearing of the fifth example was disassembled, it was observed that wear debris had accumulated on the curved surface groove portion of the spacer sliding with the rollers. On the other hand, no wear powder was found in the bearing of the fifth embodiment. This is a proof that wear debris generated in the bearing of the fifth embodiment causes early locking of the bearing. In addition, the bearing life ratio of the fifth embodiment is 9.2, which is longer than the bearing life ratio of the second conventional example of 5.1, and the number of rollers increases.
By preventing the roller skew, the life is extended.

【００２９】次に、本発明の第６の実施例について説明
する。第６の実施例では、第５の実施例に加え、スペー
サ６表面に二硫化モリブデンを１μｍの膜厚で被覆した
ものである。軸受寿命を評価した結果を表４に示す。Next, a sixth embodiment of the present invention will be described. In the sixth embodiment, in addition to the fifth embodiment, the surface of the spacer 6 is coated with molybdenum disulfide to a film thickness of 1 μm. Table 4 shows the results of evaluating the bearing life.

【００３０】[0030]

【表４】 [Table 4]

【００３１】第６の実施例では軸受寿命比が１３．４で
あり、スペーサ表面に二硫化モリブデンを被覆していな
い第５の実施例の寿命比９，２と比べると、寿命延長の
効果が認められた。このように、第６の実施例はスペー
サ６表面の二硫化モリブデンが潤滑剤の供給源となり軸
受寿命を延長することができる。In the sixth embodiment, the bearing life ratio is 13.4. Compared with the life ratio 9,2 of the fifth embodiment in which the spacer surface is not coated with molybdenum disulfide, the life extension effect is improved. Admitted. As described above, in the sixth embodiment, the molybdenum disulfide on the surface of the spacer 6 serves as a lubricant supply source to extend the life of the bearing.

【００３２】次に、本発明の第７の実施例について説明
する。第７の実施例では、第６の実施例でスペーサの表
面に被覆した二硫化モリブデンの膜中に酸素を１０％添
加したものである。軸受寿命を評価した結果を表４に併
せて示す。第７の実施例では軸受寿命比が４２．８であ
るため、酸素を添加していない第６の実施例の寿命比１
３．４と比べると、寿命延長の効果が顕著に認められ
た。このように、第７の実施例は、膜中に酸素を添加す
ると、膜が剥がれ易くなると共に、供給源としての効果
が大きくなり、軸受寿命を延長することができる。Next, a seventh embodiment of the present invention will be described. In the seventh embodiment, 10% of oxygen is added to the molybdenum disulfide film coated on the surface of the spacer in the sixth embodiment. The results of evaluating the bearing life are also shown in Table 4. Since the bearing life ratio is 42.8 in the seventh embodiment, the life ratio 1 of the sixth embodiment in which oxygen is not added is 1
Compared with 3.4, the effect of extending the life was remarkably recognized. As described above, in the seventh embodiment, when oxygen is added to the film, the film is easily peeled off, the effect as a supply source is increased, and the life of the bearing can be extended.

【００３３】本発明の第８の実施例について説明する。
第８の実施例では、スペーサをポリエーテルエーテルケ
トン樹脂とポリテトラフルオロエチレン樹脂とアラミド
繊維の樹脂材料に二硫化モリブデンを含有させた複合材
料で形成した軸受を寿命評価した。評価結果を表４に併
せて示している。第８の実施例の軸受寿命比が１３．６
であるため、第５の実施例の寿命比９．２と比べると、
寿命延長の効果が認められた。このように、第８の実施
例はスペーサを二硫化モリブデンを含有した樹脂材料で
構成したので、二硫化モリブデンと樹脂材料の潤滑成分
が長期にわたり、潤滑供給源して働き、軸受の寿命を延
ばすことができる。An eighth embodiment of the present invention will be described.
In the eighth example, the life of the bearing was evaluated, in which the spacer was formed of a composite material in which molybdenum disulfide was contained in a resin material of polyetheretherketone resin, polytetrafluoroethylene resin, and aramid fiber. The evaluation results are also shown in Table 4. The bearing life ratio of the eighth embodiment is 13.6.
Therefore, compared with the life ratio 9.2 of the fifth embodiment,
The effect of extending the life was recognized. As described above, in the eighth embodiment, since the spacer is made of the resin material containing molybdenum disulfide, the lubricating component of the molybdenum disulfide and the resin material works as a lubricating supply source for a long period of time to extend the life of the bearing. be able to.

【００３４】次に、本発明の第９の実施例を説明する。
図５は第９の実施例を示すクロスローラ軸受の側面展開
図で、図６は図５のＡ−Ａ線に沿う拡大断面図である。
図において、７はスペーサである。第９の実施例が第４
の実施例と異なるのはスペーサ７の形状を円柱状とした
点である。本実施例も第４の実施例と同じく、設計およ
び組立上の理由で、直径はころの直径の２０〜４８％の
範囲と決まる。このように、第９の実施例は、第４の実
施例と同じ作用で摩耗粉が過大に発生せず、ころのスキ
ューが生じず、軸受の負荷容量を増やすことができる。Next, a ninth embodiment of the present invention will be described.
FIG. 5 is a side development view of a cross roller bearing showing a ninth embodiment, and FIG. 6 is an enlarged sectional view taken along the line AA of FIG.
In the figure, 7 is a spacer. The ninth embodiment is the fourth
What is different from the embodiment is that the spacer 7 has a cylindrical shape. Like the fourth embodiment, this embodiment has a diameter of 20 to 48% of the diameter of the roller for design and assembly reasons. As described above, in the ninth embodiment, the same action as that of the fourth embodiment does not cause excessive generation of abrasion powder, the roller skew does not occur, and the load capacity of the bearing can be increased.

【００３５】[0035]

【発明の効果】以上述べたように、本発明によれば、以
下の効果がある。 （１）第１の実施例〜第３の実施例は、ころ軸受のスペ
ーサを球状としたため、摩耗粉の発生を減少させ、摩耗
粉かみこみによる軸受の早期ロックを無くすことができ
る。また、スペーサ表面に二硫化モリブデンを被覆した
ため、その膜が潤滑剤の供給源となり軸受の寿命を延ば
すことができる。さらに、二硫化モリブデンの膜中に酸
素、窒素、炭素、またはホウ素のいずれかの元素を含め
たため、膜が剥がれ易くなり、供給源としての効果が大
きくなると共に、軸受の寿命をさらに延ばすことができ
る。As described above, the present invention has the following effects. (1) In the first to third embodiments, since the spacer of the roller bearing is spherical, the generation of wear debris can be reduced, and the early locking of the bearing due to the inclusion of wear debris can be eliminated. Further, since the spacer surface is coated with molybdenum disulfide, the film serves as a supply source of the lubricant, and the life of the bearing can be extended. Further, since the element of oxygen, nitrogen, carbon, or boron is included in the molybdenum disulfide film, the film is easily peeled off, the effect as a supply source is increased, and the life of the bearing is further extended. it can.

【００３６】（２）第４の実施例〜第９の実施例は、こ
ろ軸受のスペーサを球状、または円柱状とし、その直径
をころの直径の２０〜４８％とし、一対のころ間に複数
個介装させたため、スキューの防止による滑り成分を減
少させると共に、摩耗粉の発生減少による軸受の早期ロ
ックを防止することができる。また、スペーサ表面に二
硫化モリブデンを被覆したため、その膜が潤滑剤の供給
源となり軸受の寿命を延ばすことができる。さらに、二
硫化モリブデンの膜中に酸素、窒素、炭素、またはホウ
素のいずれかの元素を含めたため、膜が剥がれ易くな
り、供給源としての効果が大きくなると共に、軸受の寿
命がさらに延ばすことができる。それから、スペーサを
二硫化モリブデン含有の樹脂材料で形成したため、これ
らの潤滑成分が長期にわたり、潤滑供給源として働き、
軸受の寿命を延ばすことができる。(2) In the fourth to ninth embodiments, the spacer of the roller bearing is spherical or cylindrical, and its diameter is 20 to 48% of the diameter of the roller. Since they are individually interposed, the slip component due to the prevention of skew can be reduced, and the early locking of the bearing due to the reduction of generation of wear powder can be prevented. Further, since the spacer surface is coated with molybdenum disulfide, the film serves as a supply source of the lubricant, and the life of the bearing can be extended. Furthermore, since the element of oxygen, nitrogen, carbon, or boron is included in the molybdenum disulfide film, the film is easily peeled off, the effect as a supply source is increased, and the life of the bearing is further extended. it can. Then, since the spacers were made of a resin material containing molybdenum disulfide, these lubricating components worked as a lubricating supply source for a long time,
The life of the bearing can be extended.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の第１の実施例〜第３の実施例に共通な
クロスローラ軸受の側面展開図で、外輪を一部切り欠い
ている。FIG. 1 is a side development view of a cross roller bearing common to the first to third embodiments of the present invention, in which an outer ring is partially cut away.

【図２】図１のＡ−Ａ線に沿う断面図である。FIG. 2 is a sectional view taken along the line AA of FIG.

【図３】本発明の第４の実施例〜第８の実施例に共通な
クロスローラ軸受の側面展開図である。FIG. 3 is a side development view of a cross roller bearing common to the fourth to eighth embodiments of the present invention.

【図４】図３のＡ−Ａ断面図である。4 is a cross-sectional view taken along the line AA of FIG.

【図５】本発明の第９の実施例を示すクロスローラ軸受
の側面展開図である。FIG. 5 is a side development view of a cross roller bearing showing a ninth embodiment of the present invention.

【図６】図５のＡ−Ａ断面図である。6 is a cross-sectional view taken along the line AA of FIG.

【図７】第１の従来例を示すクロスローラ軸受であっ
て、（ａ）はその一部を示す平面図、（ｂ）はスペーサ
の斜視図である。FIG. 7 is a cross roller bearing showing a first conventional example, in which (a) is a plan view showing a part thereof and (b) is a perspective view of a spacer.

【図８】クロスローラ軸受の側面展開図である。FIG. 8 is a side development view of a cross roller bearing.

【図９】第２の従来例を示すクロスローラ軸受の側面展
開図である。FIG. 9 is a side development view of a cross roller bearing showing a second conventional example.

【図１０】第１の比較例を示す玉軸受の正断面図であ
る。FIG. 10 is a front sectional view of a ball bearing showing a first comparative example.

【符号の説明】[Explanation of symbols]

１ 内輪 ２ 外輪 ３ 内輪転走溝 ４ 外輪転走溝 ５ ころ ６ スペーサ ７ スペーサ 1 inner ring 2 outer ring 3 Inner ring rolling groove 4 Outer ring rolling groove Around 5 6 spacers 7 Spacer

Claims (5)

【特許請求の範囲】[Claims] 【請求項１】 内輪と外輪と、前記内輪と前記外輪のそ
れぞれ対向する面に設けた内輪転走溝と外輪転走溝と、
前記二つの転走溝の間に挿入した複数個のころを備え、
これら構成部品の表面の一部または全部に固体潤滑剤の
被膜を形成し、前記ころ間に介装させて保持するスペー
サとからなる固体潤滑ころ軸受において、 前記スペーサが球状または円柱状であることを特徴とす
る固体潤滑ころ軸受。1. An inner ring and an outer ring, and an inner ring rolling groove and an outer ring rolling groove provided on surfaces of the inner ring and the outer ring facing each other, respectively.
With a plurality of rollers inserted between the two rolling grooves,
In a solid lubricating roller bearing comprising a spacer formed by forming a coating of a solid lubricant on a part or all of the surfaces of these components, and holding the spacer by interposing between the rollers, the spacer is spherical or cylindrical. Solid lubricated roller bearings. 【請求項２】 前記スペーサの直径が前記ころの直径の
２０％〜４８％であり、一対のころ間に介装させる前記
スペーサの個数が複数であることを特徴とする請求項１
記載の固体潤滑ころ軸受。2. The diameter of the spacer is 20% to 48% of the diameter of the roller, and the number of the spacers interposed between the pair of rollers is plural.
The solid lubricated roller bearing described. 【請求項３】 前記スペーサの表面に二硫化モリブデン
を被覆したことを特徴とする請求項１または２記載の固
体潤滑ころ軸受。3. The solid lubricated roller bearing according to claim 1, wherein the surface of the spacer is coated with molybdenum disulfide. 【請求項４】 前記スペーサの表面に被覆した二硫化モ
リブデンの膜中に酸素、窒素、炭素、またはホウ素のい
ずれかの元素を含むことを特徴とする請求項３記載の固
体潤滑ころ軸受。4. The solid lubricated roller bearing according to claim 3, wherein an element of oxygen, nitrogen, carbon or boron is contained in the molybdenum disulfide film coated on the surface of the spacer. 【請求項５】 前記スペーサは二硫化モリブデンを含有
した樹脂材料からなることを特徴とする請求項１または
２記載の固体潤滑ころ軸受。5. The solid lubricated roller bearing according to claim 1, wherein the spacer is made of a resin material containing molybdenum disulfide.
JP2002109548A 2002-04-11 2002-04-11 Solid lubricated roller bearing Expired - Fee Related JP3981814B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2002109548A JP3981814B2 (en) 2002-04-11 2002-04-11 Solid lubricated roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2002109548A JP3981814B2 (en) 2002-04-11 2002-04-11 Solid lubricated roller bearing

Publications (2)

Publication Number Publication Date
JP2003301851A true JP2003301851A (en) 2003-10-24
JP3981814B2 JP3981814B2 (en) 2007-09-26

Family

ID=29392981

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2002109548A Expired - Fee Related JP3981814B2 (en) 2002-04-11 2002-04-11 Solid lubricated roller bearing

Country Status (1)

Country Link
JP (1) JP3981814B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104033496A (en) * 2014-05-23 2014-09-10 洛阳吉瑞特轴承制造有限公司 Outer ring of cylindrical roller bearing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104033496A (en) * 2014-05-23 2014-09-10 洛阳吉瑞特轴承制造有限公司 Outer ring of cylindrical roller bearing

Also Published As

Publication number Publication date
JP3981814B2 (en) 2007-09-26

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