JP2007232190A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2007232190A
JP2007232190A JP2006058160A JP2006058160A JP2007232190A JP 2007232190 A JP2007232190 A JP 2007232190A JP 2006058160 A JP2006058160 A JP 2006058160A JP 2006058160 A JP2006058160 A JP 2006058160A JP 2007232190 A JP2007232190 A JP 2007232190A
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Prior art keywords
spacer
collar
inner ring
rolling
outer ring
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JP2006058160A
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JP4554539B2 (en
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Takuya Ozu
琢也 小津
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/40—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 with loose spacing bodies between 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
    • 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
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing wherein spacers are laid between rolling elements and guided along the collar inner diameter face of an outer ring or the collar outer diameter face of an inner ring, avoiding stepped wear on the guide faces of the spacers. <P>SOLUTION: The rolling bearing comprises the plurality of rolling elements 6 rollingly laid between an inner ring raceway surface and an outer ring raceway surface, and the spacers 8 located between the adjacent rolling elements 6. The spacers 8 are guided along the collar inner diameter face of the outer ring 4 or the collar outer diameter face of the inner ring 2. The spacer 8 are guided along the face of the outer ring 4 except the angle part of a collar or the face of the inner ring 2 except the angle part of a collar. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、保持器に代えて転動体間に間座を介在させた転がり軸受に関する。   The present invention relates to a rolling bearing in which a spacer is interposed between rolling elements instead of a cage.

特許文献１に、保持器に代えて隣り合う転動体間に間座を介在させた転がり軸受が例示されている。この種の転がり軸受は、軸受内により多くの転動体を組み込むことができ、高い負荷容量を得ることができる。しかしながら、特許文献１に記載された転がり軸受は、間座の動きを内輪および外輪の軌道面とつば側面によって規制するため、必然的に転動体の径方向断面と同程度の大きさの間座を介在させることになり、潤滑油の攪拌抵抗が大きい傾向がある。さらに、間座を内輪または外輪の軌道面に摺動させるため、転がり面における円滑な油膜形成が損なわれる可能性がある。
特許第３５４９５３０号公報 Patent Document 1 illustrates a rolling bearing in which a spacer is interposed between adjacent rolling elements instead of a cage. This type of rolling bearing can incorporate more rolling elements in the bearing, and can obtain a high load capacity. However, the rolling bearing described in Patent Document 1 inevitably restricts the movement of the spacer by the raceway surface and the collar side surface of the inner ring and the outer ring, so that the spacer is necessarily the same size as the radial cross section of the rolling element. Therefore, there is a tendency that the stirring resistance of the lubricating oil is large. Furthermore, since the spacer is slid on the raceway surface of the inner ring or the outer ring, smooth oil film formation on the rolling surface may be impaired.
Japanese Patent No. 3549530

そこで、間座を軌道面ではなく、外輪つば内径面または内輪つば外径面に案内させることで、上述の問題点を除去することができるが、この場合、間座の段付き磨耗が懸念される。すなわち、軌道輪のつば部は軸受の径方向に突出した形状であるため、間座を局部的に磨耗させ、その結果、間座に段差が生じてしまう。例えば、案内面となる間座の上面（外径面）または下面（内径面）が、外輪つば内径面または内輪つば外径面に対して、軸方向に一様な面で形成されている場合（図５参照）、前記段付き磨耗によって間座の軸方向への自由度が失われ（間座と軌道輪のつば側面が、すきまを持たずに摺動するため）、軸受の回転を妨げたり異常な発熱を引き起こす原因となりうる。   Therefore, the above-mentioned problem can be eliminated by guiding the spacer to the outer ring collar inner surface or the inner ring collar outer surface instead of the raceway surface, but in this case, there is a concern about the step wear of the spacer. The That is, since the collar portion of the bearing ring has a shape protruding in the radial direction of the bearing, the spacer is locally worn, and as a result, a step is generated in the spacer. For example, when the upper surface (outer diameter surface) or lower surface (inner diameter surface) of the spacer serving as the guide surface is formed as a uniform surface in the axial direction with respect to the inner diameter surface of the outer ring collar or the outer diameter surface of the inner ring collar (Refer to Fig. 5) The degree of freedom of the spacer in the axial direction is lost due to the stepped wear (because the flange and the collar side surface of the race ring slide without gaps), preventing rotation of the bearing. Or cause abnormal fever.

本発明の主要な目的は、転動体間に間座を介在させ、前記間座を外輪つば内径面または内輪つば外径面で案内する転がり軸受において、間座の案内面における段付き磨耗を回避することにある。   The main object of the present invention is to avoid stepped wear on the guide surface of the spacer in a rolling bearing in which a spacer is interposed between the rolling elements and the spacer is guided by the inner diameter surface of the outer ring collar or the outer diameter surface of the inner ring collar. There is to do.

請求項１の発明は、内輪軌道面と外輪軌道面との間に転動自在に介在する複数の転動体と、隣り合う転動体間に間座を具備し、前記間座が外輪つば内径面に案内される転がり軸受において、間座が外輪のつばの角部を避けた面にて案内されることを特徴とするものである。ここで、外輪のつばの角部とは、外輪のつば内径面の軸方向内端を指し、例えば円筒ころ軸受の場合は、外輪のつばの内径面と内側側面との境界を指し、玉軸受の場合は、軌道面との境界部に位置する角部を指す。本発明仕様は、例えば間座の上面（外径面）を凹形状で形成し、その軸方向終端だけを案内させたり、あるいは、間座の案内面（拡張部の上面）を外輪つば内径面に向かって部分的に突出させるなど、間座の上面のうちの中央部をその両側の拡張部よりも一段低くすることで得ることができる。   The invention according to claim 1 comprises a plurality of rolling elements that are freely rollable between the inner ring raceway surface and the outer ring raceway surface, and a spacer between the adjacent rolling elements, the spacer being an outer ring collar inner diameter surface. In the rolling bearing guided by the above, the spacer is guided by a surface that avoids the corners of the collar of the outer ring. Here, the corner portion of the collar of the outer ring refers to the inner end in the axial direction of the inner diameter surface of the collar of the outer ring. For example, in the case of a cylindrical roller bearing, it refers to the boundary between the inner surface of the outer ring collar and the inner side surface. In the case of, it refers to the corner located at the boundary with the track surface. The specification of the present invention is such that, for example, the upper surface (outer diameter surface) of the spacer is formed in a concave shape and only the axial end is guided, or the guide surface of the spacer (upper surface of the expansion portion) is used as the inner ring surface It can be obtained by making the central part of the upper surface of the spacer a step lower than the extended parts on both sides, such as partially projecting toward the surface.

請求項３の発明は、内輪軌道面と外輪軌道面との間に転動自在に介在する複数の転動体と、隣り合う転動体間に間座を具備し、前記間座が内輪つば外径面に案内される転がり軸受において、前記間座が内輪のつばの角部を避けた面にて案内されることを特徴とするものである。ここで、内輪のつばの角部とは、内輪のつばの外径面の軸方向内端を指し、例えば円筒ころ軸受の場合は、内輪のつばの外径面と内側側面との境界を指し、玉軸受の場合は、軌道面との境界部に位置する角部を指す。   The invention of claim 3 comprises a plurality of rolling elements that are freely rollable between the inner ring raceway surface and the outer ring raceway surface, and a spacer between adjacent rolling elements, wherein the spacer has an inner ring collar outer diameter. In a rolling bearing guided by a surface, the spacer is guided by a surface that avoids the corners of the collar of the inner ring. Here, the corner of the collar of the inner ring refers to the inner end in the axial direction of the outer diameter surface of the collar of the inner ring.For example, in the case of a cylindrical roller bearing, it refers to the boundary between the outer diameter surface of the inner ring and the inner side surface. In the case of a ball bearing, it refers to the corner located at the boundary with the raceway surface.

請求項１および請求項３に記載した構成を採用することで、間座の案内面における段付き磨耗を回避することができる。すなわち、上記仕様によれば、間座の案内面（拡張部の上面）が磨耗しても段付き部が形成されないため、間座の軸方向への自由度が失われることはない。さらに、間座の上面のうちの中央部をその両側の拡張部よりも一段低くすることにより、間座が転動体を覆う範囲が縮小されるため、潤滑油による転動体の冷却効率が向上する。   By adopting the configuration described in claims 1 and 3, stepped wear on the guide surface of the spacer can be avoided. That is, according to the above specifications, the stepped portion is not formed even if the guide surface of the spacer (the upper surface of the extended portion) is worn, so that the degree of freedom in the axial direction of the spacer is not lost. Further, by lowering the central portion of the upper surface of the spacer one step lower than the extended portions on both sides thereof, the range in which the spacer covers the rolling elements is reduced, so that the cooling efficiency of the rolling elements by the lubricating oil is improved. .

請求項２の発明は、請求項１の転がり軸受において、前記間座の外輪つば内径面に向かい合う案内面を、外輪つば内径面の曲率半径よりも小さい凸曲面で形成したことを特徴とするものである。また、請求項４の発明は、請求項３の転がり軸受において、前記間座の内輪つば外径面に向かい合う案内面を、内輪つば外径面の曲率半径よりも大きい凹曲面で形成したことを特徴とするものである。このような構成を採用することで、前記案内面にいわゆる「くさび効果」（運動方向に狭まっているくさび状のすきまに、流体が粘性によって引き込まれて圧力すなわち負荷能力を発生する効果）が発生し、案内面における油膜切れの発生および間座の磨耗を軽減することができる。   According to a second aspect of the present invention, in the rolling bearing of the first aspect, the guide surface facing the inner ring surface of the outer ring collar of the spacer is formed with a convex curved surface that is smaller than the radius of curvature of the inner ring surface of the outer ring collar. It is. According to a fourth aspect of the present invention, in the rolling bearing of the third aspect, the guide surface that faces the outer diameter surface of the inner ring collar of the spacer is formed as a concave curved surface that is larger than the radius of curvature of the outer diameter surface of the inner ring collar. It is a feature. By adopting such a configuration, a so-called “wedge effect” (an effect in which a fluid is drawn into the wedge-shaped gap narrowing in the movement direction by viscosity to generate pressure, that is, load capacity) occurs on the guide surface. In addition, the occurrence of oil film breakage on the guide surface and wear of the spacer can be reduced.

請求項５の発明は、請求項１ないし４のいずれかの転がり軸受において、前記間座の、転動体と向き合う面が、転動体のピッチ円を跨いで延在する凹形状を有し、間座を隣り合う転動体で挟み込んだとき、間座と前記軌道輪との間にすきまを有することを特徴とするものである。軌道面上で前記間座を転動体で挟み込むと、前記凹形状の底を接触位置として間座の径方向位置が決まる。そのとき、間座と軌道輪の間にすきまを有するように設定することで、間座が隣り合う転動体によって軌道輪に押し付けられる状態を回避することができる。すなわち、上記設定により間座は基本的には転動体案内となり、円周方向すきまに位置する間座だけが隣り合う転動体の拘束から解放され、回転速度が高い場合には外輪に、低い場合には転動体または内輪に案内される仕様となる。解放された間座には、自重、遠心力以外に半径方向への力が作用しないため、案内面における発熱および間座の磨耗を軽減させることができる。   The invention according to claim 5 is the rolling bearing according to any one of claims 1 to 4, wherein a surface of the spacer facing the rolling element has a concave shape extending across the pitch circle of the rolling element. When the seat is sandwiched between adjacent rolling elements, a gap is provided between the spacer and the raceway. When the spacer is sandwiched between rolling elements on the raceway surface, the radial position of the spacer is determined with the concave bottom as a contact position. At that time, by setting the clearance between the spacer and the raceway, it is possible to avoid a state where the spacer is pressed against the raceway by the adjacent rolling elements. That is, with the above settings, the spacer is basically a rolling element guide, and only the spacer positioned in the circumferential clearance is released from the restraint of the adjacent rolling elements, and when the rotational speed is high, the outer ring is low. The specification is guided to the rolling elements or the inner ring. Since the radial force other than its own weight and centrifugal force does not act on the released spacer, heat generation on the guide surface and wear of the spacer can be reduced.

請求項６の発明は、請求項１ないし５のいずれかの転がり軸受において、前記間座の軸方向両端に、ころ端面と向かい合う拡張部を設けたことを特徴とするものである。このような構成を採用することで、前記案内面積が拡大し、案内面において油膜が形成されやすくなり、発熱および間座の磨耗を軽減させることができる。   According to a sixth aspect of the present invention, in the rolling bearing according to any one of the first to fifth aspects, extended portions facing the roller end faces are provided at both axial ends of the spacer. By adopting such a configuration, the guide area is increased, an oil film is easily formed on the guide surface, and heat generation and wear of the spacer can be reduced.

本発明によれば、転動体間に間座を介在せ、前記間座を外輪つば内径面または内輪つば外径面で案内させる転がり軸受において、間座の案内面における段付き磨耗を回避し、さらには、案内面における発熱や間座の磨耗を軽減させることができ、長期間円滑に回転する転がり軸受を提供することができる。   According to the present invention, in a rolling bearing in which a spacer is interposed between the rolling elements and the spacer is guided by the inner ring collar inner surface or the inner ring collar outer diameter surface, the stepped wear on the guide surface of the spacer is avoided. Furthermore, heat generation on the guide surface and wear of the spacer can be reduced, and a rolling bearing that rotates smoothly for a long period of time can be provided.

以下、本発明の実施の形態について、図面を参照して説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１および図２に示す実施の形態はＮＪタイプの円筒ころ軸受に適用した例であり、この円筒ころ軸受は、内輪２と、外輪４と、円筒ころ６と、間座８とで構成されている。内輪は片つば付きで、外輪４は両つば付きである。円筒ころ６は内輪２の軌道面と外輪４の軌道面との間で転動自在で、隣り合う円筒ころ６間に間座８が介在させてある。間座８は概ね板状で、その両面に円筒ころ６の転動面６ａと接触する面すなわちころ接触面８ａを有する。間座８の長手方向の両端には、円筒ころ６のころ端面６ｂと向かい合う面をもった拡張部８ｂが形成してある。   The embodiment shown in FIGS. 1 and 2 is an example applied to an NJ type cylindrical roller bearing, and this cylindrical roller bearing includes an inner ring 2, an outer ring 4, a cylindrical roller 6, and a spacer 8. ing. The inner ring has one collar and the outer ring 4 has both collars. The cylindrical roller 6 can roll between the raceway surface of the inner ring 2 and the raceway surface of the outer ring 4, and a spacer 8 is interposed between the adjacent cylindrical rollers 6. The spacer 8 is generally plate-shaped, and has a surface that contacts the rolling surface 6a of the cylindrical roller 6, that is, a roller contact surface 8a, on both surfaces thereof. At both ends in the longitudinal direction of the spacer 8, extended portions 8 b having surfaces facing the roller end surface 6 b of the cylindrical roller 6 are formed.

各拡張部８ｂは外輪４のつば４ａの内径面と向かい合っており、軸受の運転中、間座８は外輪４のつば４ａの内径面にて案内される。ここで、図１から分かるとおり、間座８の上面すなわち軸受の半径方向外側の面は、拡張部８ｂを除き、緩やかな勾配をもつ凹形状に形成されており、間座８の上面の勾配は外輪４のつば４ａの内径面の途中の位置から開始している。言い換えれば、間座８の各拡張部８ｂの長さは外輪４のつば４ａの内径面の幅よりも短い。したがって、間座８が、外輪４のつば４ａの内径面と内側側面との角部（つば肩部）と接触することはない。なお、この実施の形態では、間座８の上面を凹形状に形成し、この凹部と拡張部の上面とを緩やかな曲線でつないであるが、前記凹形状の底面と拡張部の上面は、勾配ではなく垂直につないでもよい。要するに、間座８の上面のうち、中央部をその両側の拡張部８ｂよりも一段低くすればよく、両者間の移行部はなだらかであっても、あるいは段差ができていてもよい。   Each expansion portion 8b faces the inner diameter surface of the collar 4a of the outer ring 4, and the spacer 8 is guided by the inner diameter surface of the collar 4a of the outer ring 4 during operation of the bearing. Here, as can be seen from FIG. 1, the upper surface of the spacer 8, that is, the radially outer surface of the bearing, is formed in a concave shape having a gentle gradient except for the extended portion 8 b, and the gradient of the upper surface of the spacer 8. Is started from a position in the middle of the inner diameter surface of the collar 4a of the outer ring 4. In other words, the length of each extended portion 8b of the spacer 8 is shorter than the width of the inner diameter surface of the collar 4a of the outer ring 4. Therefore, the spacer 8 does not come into contact with the corner (rib shoulder) between the inner diameter surface and the inner side surface of the collar 4a of the outer ring 4. In this embodiment, the upper surface of the spacer 8 is formed in a concave shape, and the concave portion and the upper surface of the extended portion are connected by a gentle curve. It may be connected vertically instead of gradient. In short, the central portion of the upper surface of the spacer 8 may be made one step lower than the extended portions 8b on both sides thereof, and the transition portion between the two may be gentle or have a step.

図３に示すように、間座８のころ転動面６ａと向き合う面すなわちころ接触面８ａはころ６のピッチ円を跨いで延在する凹形状である。間座８が外輪つば内径面によって案内され、隣り合うころ６で間座８を挟み込んだとき、間座８と外輪４との間にすきまＳｒがある。図４に示すように、外輪４の軌道面上で間座８をころ６で挟み込むと、外輪４のつば内径面の凹形状の底を接触位置として間座８の半径方向位置が決まる。そのとき、間座８と外輪４との間にすきまＳｒが存在するように設定することで、間座８が隣り合うころ６によって外輪４に押し付けられる状態（図４参照）を回避することができる。すなわち、上記設定により間座８は基本的にはころ案内となり、円周方向すきまに位置する間座８だけが隣り合うころ６の拘束から解放され、回転速度が高い場合には、自重、遠心力以外に半径方向への力が作用しないため、間座８の案内面（外輪つば内径面と向き合う拡張部の上面）における発熱や磨耗を軽減させることができる。   As shown in FIG. 3, the surface of the spacer 8 that faces the roller rolling surface 6 a, that is, the roller contact surface 8 a has a concave shape that extends across the pitch circle of the roller 6. The spacer 8 is guided by the inner surface of the outer ring collar, and when the spacer 8 is sandwiched between the adjacent rollers 6, there is a clearance Sr between the spacer 8 and the outer ring 4. As illustrated in FIG. 4, when the spacer 8 is sandwiched between the rollers 6 on the raceway surface of the outer ring 4, the radial position of the spacer 8 is determined with the concave bottom of the collar inner diameter surface of the outer ring 4 as the contact position. At that time, by setting so that the clearance Sr exists between the spacer 8 and the outer ring 4, it is possible to avoid a state in which the spacer 8 is pressed against the outer ring 4 by the adjacent rollers 6 (see FIG. 4). it can. In other words, the spacer 8 is basically a roller guide by the above setting, and only the spacer 8 positioned in the circumferential clearance is released from the restraint of the adjacent roller 6, and when the rotational speed is high, Since no force in the radial direction other than the force acts, heat generation and wear on the guide surface of the spacer 8 (the upper surface of the extended portion facing the inner surface of the outer ring collar) can be reduced.

図３から分かるように、間座８の案内面（外輪つば内径面と向き合う面）は、外輪つば内径面の曲率半径Ｒ２よりも小さい曲率半径Ｒ１の凸曲面である。なお、図示は省略したが、間座の拡張部を内輪つば外径側に配置する場合、間座８の内輪つば外径面と向き合う面を、内輪つば外径の曲率半径よりも大きい曲率半径の凹曲面とすることもできる。このような構成を採用することで、いわゆる「くさび効果」（運動方向に狭まっているくさび状のすきまに、流体が粘性によって引き込まれて圧力すなわち負荷能力を発生する効果）が得られ、間座の案内面における発熱や磨耗を軽減させることができる。   As can be seen from FIG. 3, the guide surface of the spacer 8 (the surface facing the inner surface of the outer ring collar) is a convex curved surface having a radius of curvature R1 smaller than the radius of curvature R2 of the inner surface of the outer ring collar. In addition, although illustration was abbreviate | omitted, when arrange | positioning the expansion part of a spacer to an inner ring collar outer diameter side, the curvature radius larger than the curvature radius of the inner ring collar outer diameter is the surface facing the inner ring collar outer diameter surface of the spacer 8 Or a concave curved surface. By adopting such a configuration, a so-called “wedge effect” (an effect in which fluid is drawn into the wedge-shaped gap narrowing in the direction of motion by viscosity to generate pressure, that is, load capacity) is obtained, and the spacer Heat generation and wear on the guide surface can be reduced.

実施例を示す円筒ころ軸受の縦断面図Vertical sectional view of cylindrical roller bearing showing an embodiment 図１の円筒ころ軸受の破断斜視図Broken perspective view of the cylindrical roller bearing of FIG. 間座のみ断面にした図１の円筒ころ軸受の部分側面図1 is a partial side view of the cylindrical roller bearing of FIG. 図１の円筒ころ軸受の部分側面図Partial side view of the cylindrical roller bearing of FIG. 比較例を示す図１と類似の縦断面図Longitudinal sectional view similar to FIG. 1 showing a comparative example

符号の説明Explanation of symbols

２ 内輪
４ 外輪
４ａ つば
６ 円筒ころ
６ａ 転動面
６ｂ ころ端面
８ 間座
８ａ ころ接触面
８ｂ 拡張部 2 Inner ring 4 Outer ring 4a Collar 6 Cylindrical roller 6a Rolling surface 6b Roller end face 8 Spacer 8a Roller contact surface 8b Expansion part

Claims (6)

内輪軌道面と外輪軌道面との間に転動自在に介在する複数の転動体と、隣り合う転動体間に間座を具備し、前記間座が外輪つば内径面に案内される転がり軸受において、間座が外輪のつばの角部を避けた面にて案内される転がり軸受。   A rolling bearing comprising a plurality of rolling elements interposed between an inner ring raceway surface and an outer ring raceway surface so as to be freely rollable, and a spacer between adjacent rolling elements, wherein the spacer is guided by an inner ring collar surface. Rolling bearings in which the spacer is guided on a surface that avoids the corners of the collar of the outer ring. 前記間座の外輪つば内径面に向かい合う案内面を、外輪つば内径面の曲率半径よりも小さい凸曲面で形成した請求項１の転がり軸受。   The rolling bearing according to claim 1, wherein the guide surface facing the inner diameter surface of the outer ring collar of the spacer is formed as a convex curved surface smaller than the radius of curvature of the inner diameter surface of the outer ring collar. 内輪軌道面と外輪軌道面との間に転動自在に介在する複数の転動体と、隣り合う転動体間に間座を具備し、前記間座が内輪つば外径面に案内される転がり軸受において、間座が内輪のつばの角部を避けた面にて案内される転がり軸受。   A rolling bearing having a plurality of rolling elements interposed between an inner ring raceway surface and an outer ring raceway surface so as to be freely rollable, and a spacer between adjacent rolling elements, the spacer being guided to an outer diameter surface of an inner ring collar. Rolling bearings in which the spacer is guided on a surface that avoids the corners of the collar of the inner ring. 前記間座の内輪つば外径面に向かい合う案内面を、内輪つば外径面の曲率半径よりも大きい凹曲面で形成した請求項２の転がり軸受。   The rolling bearing according to claim 2, wherein the guide surface facing the outer diameter surface of the inner ring collar of the spacer is formed as a concave curved surface larger than the radius of curvature of the outer diameter surface of the inner ring collar. 前記間座の、転動体と向き合う面が、転動体のピッチ円を跨いで延在する凹形状を有し、間座を隣り合う転動体で挟み込んだとき、間座と前記軌道輪との間にすきまを有する請求項１ないし４のいずれかの転がり軸受。   The face of the spacer facing the rolling element has a concave shape extending across the pitch circle of the rolling element, and when the spacer is sandwiched between adjacent rolling elements, the space between the spacer and the raceway The rolling bearing according to claim 1, which has a clearance. 前記間座の軸方向両端に、ころ端面と向かい合う拡張部を設けた請求項１ないし５のいずれかの転がり軸受。   The rolling bearing according to any one of claims 1 to 5, wherein expansion portions facing the roller end faces are provided at both axial ends of the spacer.
JP2006058160A 2006-03-03 2006-03-03 Rolling bearing Active JP4554539B2 (en)

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5415144U (en) * 1977-07-02 1979-01-31
JPS5493646U (en) * 1977-12-15 1979-07-03
JPH0217218A (en) * 1988-07-05 1990-01-22 Koyo Seiko Co Ltd Roll bearing
JPH0658334A (en) * 1992-08-07 1994-03-01 Nippon Seiko Kk Radial bearing to suppress squeak
JPH084773A (en) * 1994-06-21 1996-01-09 Ntn Corp Solid lubricating rolling bearing
JPH09242759A (en) * 1996-03-11 1997-09-16 Nippon Seiko Kk Roller bearing
JPH1162995A (en) * 1997-08-28 1999-03-05 Nippon Seiko Kk Rolling bearing
JPH11280769A (en) * 1998-03-27 1999-10-15 Nippon Seiko Kk Roller bearing
JP2000320548A (en) * 1999-05-13 2000-11-24 Koyo Seiko Co Ltd Rolling bearing
JP2007232187A (en) * 2006-03-03 2007-09-13 Ntn Corp Cylindrical roller bearing for transmission

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5415144U (en) * 1977-07-02 1979-01-31
JPS5493646U (en) * 1977-12-15 1979-07-03
JPH0217218A (en) * 1988-07-05 1990-01-22 Koyo Seiko Co Ltd Roll bearing
JPH0658334A (en) * 1992-08-07 1994-03-01 Nippon Seiko Kk Radial bearing to suppress squeak
JPH084773A (en) * 1994-06-21 1996-01-09 Ntn Corp Solid lubricating rolling bearing
JPH09242759A (en) * 1996-03-11 1997-09-16 Nippon Seiko Kk Roller bearing
JPH1162995A (en) * 1997-08-28 1999-03-05 Nippon Seiko Kk Rolling bearing
JPH11280769A (en) * 1998-03-27 1999-10-15 Nippon Seiko Kk Roller bearing
JP2000320548A (en) * 1999-05-13 2000-11-24 Koyo Seiko Co Ltd Rolling bearing
JP2007232187A (en) * 2006-03-03 2007-09-13 Ntn Corp Cylindrical roller bearing for transmission

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