JP4708222B2 - Roller bearing - Google Patents

Roller bearing Download PDF

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JP4708222B2
JP4708222B2 JP2006058153A JP2006058153A JP4708222B2 JP 4708222 B2 JP4708222 B2 JP 4708222B2 JP 2006058153 A JP2006058153 A JP 2006058153A JP 2006058153 A JP2006058153 A JP 2006058153A JP 4708222 B2 JP4708222 B2 JP 4708222B2
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spacer
bearing
roller
facing
radial direction
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JP2007232188A (en
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琢也 小津
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NTN Corp
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NTN Corp
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/37Loose spacing bodies
    • F16C33/3706Loose 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings 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
    • F16C19/24Bearings 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
    • F16C19/26Bearings 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings 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
    • F16C19/40Bearings 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

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

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ころ軸受に関する。   The present invention relates to a roller bearing in which a spacer is interposed between rolling elements instead of a cage.

特許文献1に、隣り合うころ間に間座を介在させたころ軸受が開示されている。この種のころ軸受は、軸受内により多くのころ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に記載されたころ軸受は、間座の動きを内輪および外輪の軌道面とつば側面とによって規制するため、必然的にころ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およびつば側面に摺動させるため、転がり面およびつば側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 discloses a roller bearing in which a spacer is interposed between adjacent rollers. This type of roller bearing can incorporate more rollers in the bearing and can obtain a high load capacity. However, the roller 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 roller. Therefore, there is a tendency that the stirring resistance of the lubricating oil is large. Further, since the spacer is slid on the raceway surface and the collar side surface of the inner ring or the outer ring, smooth oil film formation on the rolling surface and the collar side surface may be impaired.
Japanese Patent No. 3549530

特許文献1に記載されたころ軸受の上記問題点を除去するべく、本出願人は先に、図7に示すように、ころ間に間座を介在させたころ軸受において、間座の軸方向両端にころ端面と向き合う面をもった拡張部を設けて、間座の軸方向への動きを規制することを提案している(特願2005−253746)。このような構成を採用することで、間座の軸方向への動きを前記拡張部ところ端面とで規制することができ、径方向への動きをころ転動面または内輪つば外径もしくは外輪つば内径にて規制することができる。すなわち、間座の移動規制手段として内輪や外輪の軌道面やつば側面を使用しないため、隣り合うころ間において、間座を広域にわたって介在させる必要がなく、潤滑油の攪拌抵抗を抑えることができ、また、転がり面およびつば側面における油膜形成を妨げることがない。さらに、間座を内輪つば外径または外輪つば内径に案内させる場合、前記拡張部はその案内面積を拡大する効果をも発揮するため、案内面において油膜が形成されやすくなる。   In order to eliminate the above-described problems of the roller bearing described in Patent Document 1, the present applicant previously described in FIG. 7 in the roller bearing in which the spacer is interposed between the rollers, the axial direction of the spacer. It has been proposed to restrict the movement of the spacer in the axial direction by providing extended portions with surfaces facing the roller end surfaces at both ends (Japanese Patent Application No. 2005-253746). By adopting such a configuration, the movement of the spacer in the axial direction can be restricted by the end portion of the expansion portion, and the movement in the radial direction can be restricted by the roller rolling surface or the inner ring collar outer diameter or outer ring collar. It can be regulated by the inner diameter. That is, since the inner ring and outer ring raceway surfaces and flange side surfaces are not used as spacer movement restricting means, there is no need to interpose the spacer over a wide area between adjacent rollers, and the stirring resistance of the lubricating oil can be suppressed. Also, oil film formation on the rolling surface and the collar side surface is not hindered. Further, when the spacer is guided to the inner ring collar outer diameter or the outer ring collar inner diameter, the expansion portion also exerts an effect of expanding the guide area, so that an oil film is easily formed on the guide surface.

本発明の主要な目的は、隣り合うころ間に間座を介在させたころ軸受において、前記間座の強度を向上させることにある。   A main object of the present invention is to improve the strength of a spacer in a roller bearing in which a spacer is interposed between adjacent rollers.

本発明は、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ころと、隣り合うころ間に間座を具備するころ軸受において、前記間座が合成樹脂の射出成形により一体的に形成された板状で、両面にころの転動面と接触するころ接触面を有し、かつ、長手方向の両端を円周方向に拡張してころ端面と向き合う面をもった拡張部が形成してあり、前記間座の軸受円周方向に垂直な断面において、前記間座の軸受半径方向の内側をく面は前記拡張部を含めて面一に形成し、前記拡張部から前記間座の軸受半径方向の外側を向く面に向けて同一の勾配でかつ面一の斜面部を形成し、または、前記間座の軸受半径方向の外側を向く面は前記拡張部を含めて面一に形成し、前記拡張部から前記間座の軸受半径方向の内側を向く面に向けて同一の勾配でかつ面一の斜面部を形成し、前記間座の、軸受半径方向の内側または外側を向く面にただ一つのゲートを設けることにより、樹脂の流動方向を間座ところとの接触線方向に対して直交させたことを特徴とするものである(請求項1)
また、本発明は、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ころと、隣り合うころ間に間座を具備するころ軸受において、前記間座が合成樹脂の射出成形により一体的に形成された板状で、両面にころの転動面と接触するころ接触面を有し、かつ、長手方向の両端を円周方向に拡張してころ端面と向き合う面をもった拡張部が形成してあり、前記間座の軸受円周方向に垂直な断面において、前記間座の軸受半径方向の外側を向く面は前記拡張部を含めて面一に形成し、前記拡張部から前記間座の軸受半径方向の内側を向く面に向けて同一の勾配でかつ面一の斜面部を形成し、前記間座の、軸受半径方向の内側または外側を向く面にただ一つのゲートを設けることにより、樹脂の流動方向を間座ところとの接触線方向に対して直交させたことを特徴とするものである(請求項2)。
このような構成を採用することで、間座の破損確立を低減することができる。すなわち、間座の上面(例えば間座の軸受半径方向の外側を向く面)または下面(例えば間座の軸受半径方向の内側を向く面)において、拡張部の付け根に段差を設けないことにより、応力の集中を回避することができる。言い換えれば、間座の応力集中の起点となる隅部の数を減らすことができる。
間座の、軸受円周方向に対して垂直な断面における構成として、間座の軸受半径方向の内側を向く面は拡張部を含めて面一に形成し、拡張部から間座の軸受半径方向の外側を向く面に向けて同一の勾配でかつ面一の斜面部を形成したもの、または、間座の軸受半径方向の外側を向く面は拡張部を含めて面一に形成し、拡張部から間座の軸受半径方向の内側を向く面に向けて同一の勾配でかつ面一の斜面部を形成したものの、どちらか一方を採用することで、前記応力集中の発生を回避しつつ、軸受の運転時における発熱を軽減することができる。すなわち、拡張部の前記勾配を、間座の軸方向中心寄りに向けて延伸させることで、拡張部を間座の内径側から外径側まで延在させる必要がないため、拡張部の軸受半径方向の大きさを小さくすることができ、潤滑油の攪拌抵抗を軽減することができる。また、前記勾配形状の延伸によって、ころ転動面と間座の接触長さを短くすることができる。さらに、間座がころ転動面を覆う面積が小さくなるため、潤滑油による冷却効率を向上させることができる。
This onset Ming, a plurality of rollers rollably interposed between the inner ring raceway surface and the outer ring raceway surface, the roller bearing having a spacer between rollers adjacent, injection molding said spacer is a synthetic resin It has a roller-shaped contact surface that contacts the rolling surface of the roller on both sides, and has a surface facing the roller end surface by extending both ends in the circumferential direction in the circumferential direction. Yes and extension forms, in a cross section perpendicular to the bearing circumferential direction of the spacer, the inner side of the bearing radial direction of the spacer toward Ku surface is formed flush, including the extension, the towards a plane from the extended portion toward the outside of the bearing radial direction of the spacer to form a slope portion of and flush with the same gradient, or surface facing the outside of the bearing radial direction of the spacer is the extension And the same from the extended part toward the inner surface of the spacer in the radial direction of the bearing. Forming an inclined surface portion of and flush with a gradient, said spacer, by providing the inside or only one gate on the surface facing the outside of the bearing radial contact line direction of the place the spacer to the resin flow direction (Claim 1) .
Further, the present invention provides a roller bearing having a plurality of rollers that are freely rollable between an inner ring raceway surface and an outer ring raceway surface, and a spacer between adjacent rollers. It is a plate that is integrally formed by molding, has roller contact surfaces that contact the roller rolling surfaces on both sides, and has a surface that faces both ends of the roller by extending both ends in the circumferential direction in the circumferential direction. An extension portion is formed, and in a cross section perpendicular to the bearing circumferential direction of the spacer, a surface facing the outer side of the spacer in the radial direction of the bearing is formed to be flush with the extension portion, and the extension Forming a slope portion having the same gradient and flush with the surface facing the inner side of the bearing in the radial direction of the spacer, and only one surface of the spacer facing the inner side or the outer side of the bearing radial direction. By providing a gate, the flow direction of the resin with respect to the contact line direction with the spacer Is characterized in that the allowed interlinked (claim 2).
By adopting such a configuration, establishment of breakage of the spacer can be reduced. That is, on the upper surface of the spacer (for example, the surface facing the outer side in the bearing radial direction of the spacer ) or the lower surface (for example, the surface facing the inner side of the bearing in the radial direction of the bearing ), Stress concentration can be avoided. In other words, it is possible to reduce the number of corners that are the starting point of stress concentration in the spacer.
As a configuration of the spacer in a cross section perpendicular to the circumferential direction of the bearing, the surface facing the inner side of the bearing in the radial direction of the spacer is formed to be flush with the extended portion and from the extended portion to the radial direction of the bearing. Formed with the same slope and the same slope toward the outside facing surface , or the face facing the outside in the bearing radial direction of the spacer is formed flush with the extended portion and expanded While forming the slope part of the same gradient and flush with the surface facing the inner side of the bearing radial direction of the spacer from the part, by adopting either one, while avoiding the occurrence of the stress concentration, Heat generation during operation of the bearing can be reduced. That is, by extending the gradient of the expansion portion toward the axial center of the spacer, it is not necessary to extend the expansion portion from the inner diameter side to the outer diameter side of the spacer, so the bearing radius of the expansion portion The size of the direction can be reduced, and the stirring resistance of the lubricating oil can be reduced. Moreover, the contact length of a roller rolling surface and a spacer can be shortened by extending | stretching of the said gradient shape. Furthermore, since the area where the spacer covers the roller rolling surface is reduced, the cooling efficiency by the lubricating oil can be improved.

例えば、図7に示すように拡張部を形成した場合、上下面の隅部に応力が集中する。間座には軸受の円周方向への圧縮応力のほかに、拡張部への曲げ応力が働くことがある。すなわち、間座は軸受の円周方向すきまにおいて自由度を有するため、間座の姿勢が乱れころ端面から拡張部に力が作用することがある。特に、前記隅部が間座の薄肉部付近に位置する場合、この隅部を起点に拡張部の付け根に亀裂が入るおそれがある。 For example, when the extended portion is formed as shown in FIG. 7, stress concentrates on the corners of the upper and lower surfaces. In addition to the compressive stress in the circumferential direction of the bearing, bending stress to the extension may act on the spacer. That is, since the spacer has a degree of freedom in the circumferential clearance of the bearing, the posture of the spacer may be disturbed, and a force may act on the extended portion from the roller end face. In particular, when the corner is located in the vicinity of the thin portion of the spacer, there is a possibility that a crack may occur at the base of the extended portion starting from the corner.

請求項の発明は、請求項1または2のころ軸受において、前記間座の長手方向の中央部で軸受半径方向内側または外側を向く面に切欠き部を設けたことを特徴とするものである。切欠き部の存在は潤滑油の攪拌抵抗を軽減するのに役立つばかりでなく、切り欠きによって形成された軸受半径方向内側または外側を向く面を、ゲートを設ける面として活用することもできる。 According to a third aspect of the present invention, in the roller bearing of the first or second aspect, a notch portion is provided on a surface facing the inner side or the outer side in the radial direction of the bearing at the central portion in the longitudinal direction of the spacer. is there. The presence of the notch not only helps to reduce the agitation resistance of the lubricating oil, but also the surface facing the inside or outside in the radial direction of the bearing formed by the notch can be used as a surface for providing the gate.

請求項の発明は、請求項1、2またはのころ軸受において、間座の拡張部ところ端面の間のすきまSaが、円周方向すきまをS、ころ長さをLw、前記間座の拡張部長さの最大値をLとしたとき、式1で表される範囲内であることを特徴とするものである。

Figure 0004708222
According to a fourth aspect of the present invention, in the roller bearing of the first , second, or third aspect, the clearance Sa between the expansion portion and the end surface of the spacer is S in the circumferential direction, Lw in the roller length, When the maximum value of the extension portion length is L, it is within the range represented by Formula 1.
Figure 0004708222

再び請求項ころ軸受に言及すると、前記間座が合成樹脂の射出成形で形成され、間座にただ一つのゲートを設けた構成を採用することにより、ウェルド部の発生を回避することができ、局部的な強度低下を回避することができる。間座が貫通孔を有する場合は、基本的にウェルドの発生は避けられないものの、1点ゲートを採用することでウェルドの発生を1箇所にとどめることができる。 Referring to the roller bearing according to claim 1 again, the spacer is formed by injection molding of synthetic resin, by adopting the configuration in which only provided one gate spacer, to avoid the occurrence of weld And local reduction in strength can be avoided. If the spacer has a through hole, although not essentially generate the weld is inevitable, it is possible to keep the weld occurred in one place by adopting a point gate.

また、前記間座の、軸受の半径方向の内側または外側を向いた面に前記ゲートを配置した構成を採用することにより、樹脂の流動方向がころと間座との接触線方向と直交することとなり、間座の圧砕強度を向上させることができる。 Further, the spacer, by adopting the configuration of arranging the gate radially inner or surface facing the outside of the bearing, the flow direction of the resin and the contact line direction of the rollers and the spacers orthogonal As a result, the crushing strength of the spacer can be improved.

一般的に、射出成形品は樹脂の流動方向よりもその直角方向への強度が低く、その傾向は繊維を配合した樹脂材料でより顕著に現れる。とくに繊維の方向に沿った線荷重を受ける場合、繊維強化の効果が十分に得られない。ここで、間座は軸受の運転中に、ころ転動面の線接触を介して圧縮力を受ける。そこで、間座中の樹脂の流動方向と、間座ところの接触線方向を直交させることで、圧砕強度を向上させることができる。なお、耐圧砕強度という点では、間座ところの接触位置全域にわたってゲートを設け、間座への圧縮力の方向と樹脂の流動方向を同一にすることが望ましいが、ゲートカットの処理やころ転動面との摺動性に問題があり、現実的ではない。   In general, an injection-molded product has a lower strength in the direction perpendicular to the flow direction of the resin, and this tendency appears more prominently in resin materials containing fibers. In particular, when receiving a line load along the direction of the fiber, the effect of fiber reinforcement cannot be obtained sufficiently. Here, the spacer receives a compressive force through the line contact of the roller rolling surface during the operation of the bearing. Therefore, the crushing strength can be improved by making the flow direction of the resin in the spacer perpendicular to the contact line direction of the spacer. In terms of the crushing strength, it is desirable to provide a gate over the entire contact position of the spacer and make the direction of compressive force to the spacer and the flow direction of the resin the same. There is a problem with slidability with the moving surface, which is not realistic.

本発明によれば、隣り合うころ間に間座を介在させたころ軸受において、間座の破損確率を低減することができる。さらに、軸受の運転時における潤滑油の攪拌抵抗を軽減できるほか、ころ転動面と間座の摺動面における発熱を軽減することができる。   According to the present invention, in a roller bearing in which a spacer is interposed between adjacent rollers, the probability of breakage of the spacer can be reduced. Further, the stirring resistance of the lubricating oil during the operation of the bearing can be reduced, and heat generation on the roller rolling surface and the sliding surface of the spacer can be reduced.

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.

まず、便宜上図2を参照してころ軸受の一例としての円筒ころ軸受について述べると、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。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。   First, for convenience, a cylindrical roller bearing as an example of a roller bearing will be described with reference to FIG. 2. The cylindrical roller bearing includes an inner ring 2, an outer ring 4, a cylindrical roller 6, and a spacer 8. 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 of the spacer 8 in the longitudinal direction, extended portions 8b having surfaces facing the roller end surface 6b of the cylindrical roller 6 are formed.

図1に示す実施例は、間座8の拡張部8を含めた上下の面を各々直線的に、つまり面一に形成した例である。図示のとおり、拡張部8の付け根には、拡張方向以外に段差(隅部)が形成されないため、応力の集中を避けることができる。 The embodiment shown in FIG. 1 is an example in which the upper and lower surfaces including the extended portion 8b of the spacer 8 are formed linearly, that is, flush with each other. As shown in the figure, since no step (corner) is formed at the base of the extended portion 8b except in the extended direction, concentration of stress can be avoided.

図3に示す実施例は、間座8の上面を拡張部8bを含めて一直線で、つまり面一に形成し、拡張部8の下面を斜面で形成した例である。この場合、斜面がころ接触面8aの領域まで一直線に、つまり面一に延びている。言い換えれば、拡張部8bの領域からころ接触面8aの領域にかけて同一の勾配である。このような構成を採用することで、矩形断面の拡張部に比べて拡張部8bの下隅部がカットされ、かつ、ころ接触面8aの両端の下隅部もカットされるため、軸受の運転時における潤滑油の攪拌抵抗が軽減するほか、ころ6の転動面6aと間座8との接触長さが短くなって発熱が軽減する。なお、図3では、前記勾配形状を緩やかな円弧を介して垂直面につなげているが、間座8の最下面まで勾配形状を延長してもよい。 Embodiment shown in FIG. 3 is a straight upper surface of the spacer 8 including an extension 8b, i.e. formed flush, an example in which the lower surface of the extension portion 8 b is formed at the slope. In this case, the slope extends in a straight line, that is, flush with the roller contact surface 8a. In other words, the gradient is the same from the region of the extended portion 8b to the region of the roller contact surface 8a. By adopting such a configuration, the lower corner portion of the extended portion 8b is cut compared to the extended portion having a rectangular cross section, and the lower corner portions of both ends of the roller contact surface 8a are also cut. In addition to reducing the agitation resistance of the lubricating oil, the contact length between the rolling surface 6a of the roller 6 and the spacer 8 is shortened to reduce heat generation. In FIG. 3, the gradient shape is connected to the vertical surface via a gentle arc, but the gradient shape may be extended to the lowermost surface of the spacer 8.

図4は、間座8が軸受の円周方向すきまの中で傾こうとする動きを、拡張部8bところ端面6bによって規制するのではなく、間座8ところ転動面6aの接触によって規制する状態を示したものであり、ころ端面6bから間座8の拡張部8bに加わる力を大幅に軽減することができる。例えば、図2に示す円筒ころ軸受NJ2324E(φ120×φ260×86)の内部諸元は、円周方向すきまS=1.5mm、ころ長さLw=62mm、間座の拡張部長さL=20mmであるため、間座8の拡張部8bところ端面6bの間のすきまSaは、0.53mm以上とすべきである。これを式で表すならば式1のとおりである。

Figure 0004708222
In FIG. 4, the movement of the spacer 8 to be inclined in the circumferential clearance of the bearing is not restricted by the extended portion 8 b and the end face 6 b but by the contact of the spacer 8 and the rolling surface 6 a. This shows the state, and the force applied from the roller end face 6b to the extended portion 8b of the spacer 8 can be greatly reduced. For example, the internal specifications of the cylindrical roller bearing NJ2324E (φ120 × φ260 × 86) shown in FIG. 2 are as follows: circumferential clearance S = 1.5 mm, roller length Lw = 62 mm, spacer extension portion length L = 20 mm. Therefore, the clearance Sa between the extended portion 8b of the spacer 8 and the end surface 6b should be 0.53 mm or more. If this is expressed by a formula, it is as shown in Formula 1.
Figure 0004708222

図5は射出成形によって形成した樹脂製間座8を示し、間座8の下面、言い換えれば軸受の半径方向内側を向いた面の1箇所に射出成形のゲート10が配置してある。なお、ここでは潤滑油の流動抵抗を低減させるため符号8cで示すように間座8の下部中央を切り欠いてあり、その切欠き部の下面にゲート10が設けてある。この間座8には、たとえば貫通孔のような、樹脂材料が二手に分かれて回り込むような部分がないため、ゲート10を1箇所とすることでウェルド部が発生しない。   FIG. 5 shows a resin spacer 8 formed by injection molding, and an injection-molded gate 10 is arranged at one position on the lower surface of the spacer 8, in other words, the surface facing the inside in the radial direction of the bearing. Here, in order to reduce the flow resistance of the lubricating oil, the lower center of the spacer 8 is notched as indicated by reference numeral 8c, and the gate 10 is provided on the lower surface of the notch. Since the spacer 8 does not have a portion in which the resin material is divided into two, such as a through hole, for example, a weld portion is not generated by setting the gate 10 to one location.

また、ゲート10を間座8の下面に配置したことにより、間座8中の樹脂の流動方向が、間座8ところ6との接触線方向に対して直交するため、間座8の圧砕強度が向上する。図6に、比較のためゲート10を間座8の端部に配置した場合を示す。この場合、矢印で示すように、樹脂の流動方向が間座8ところ6との接触線方向と平行になるため、間座8の圧砕強度面から望ましくない。なお、ゲート10は他の部品との接触部を避けた位置に設けるべきであり、また、軸受に組み込んだ際に目立たない場所に設けるのが望ましい。図6に関連して上に述べた理由から両端部が除かれ、ころ6と接触するという理由からころ接触面8aが除かれる結果、間座8の下面(図5)または上面がゲート10を設けるのに適していると言える。これらは軸受の半径方向の内側または外側を向いた面である。   Further, since the gate 10 is arranged on the lower surface of the spacer 8, the flow direction of the resin in the spacer 8 is orthogonal to the contact line direction with the spacer 8 and 6. Will improve. FIG. 6 shows a case where the gate 10 is arranged at the end of the spacer 8 for comparison. In this case, as indicated by the arrows, the flow direction of the resin is parallel to the contact line direction between the spacers 8 and 6, which is not desirable from the viewpoint of the crushing strength of the spacers 8. It should be noted that the gate 10 should be provided at a position that avoids contact with other components, and is preferably provided at a place that is not conspicuous when assembled in the bearing. Both ends are removed for the reasons described above in connection with FIG. 6 and the roller contact surface 8a is removed for contact with the roller 6, so that the lower surface (FIG. 5) or upper surface of the spacer 8 is the gate 10 It can be said that it is suitable for installation. These are the surfaces facing inward or outward in the radial direction of the bearing.

(A)は実施例を示す間座の正面図、(B)は斜視図(A) is the front view of the spacer which shows an Example, (B) is a perspective view. 別の実施例を示すころ軸受の破断斜視図Broken perspective view of a roller bearing showing another embodiment 図2の軸受における間座の正面図Front view of the spacer in the bearing of FIG. 間座を介して隣り合ったころを示す平面図Plan view showing rollers adjacent to each other via a spacer 別の実施例を示す間座の斜視図A perspective view of a spacer showing another embodiment 比較例を示す間座の斜視図A perspective view of a spacer showing a comparative example (A)はころ軸受の破断斜視図、(B)は図7(A)の軸受における間座の正面図(A) is a broken perspective view of a roller bearing, (B) is a front view of a spacer in the bearing of FIG. 7 (A).

符号の説明Explanation of symbols

2 内輪
4 外輪
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
8c 切欠き
10 ゲート
2 Inner ring 4 Outer ring 6 Cylindrical roller 6a Rolling surface 6b Roller end surface 8 Spacer 8a Roller contact surface 8b Expansion portion 8c Notch 10 Gate

Claims (4)

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ころと、隣り合うころ間に間座を具備するころ軸受において、
前記間座が合成樹脂の射出成形により一体的に形成された板状で、両面にころの転動面と接触するころ接触面を有し、かつ、長手方向の両端を円周方向に拡張してころ端面と向き合う面をもった拡張部が形成してあり、
前記間座の軸受円周方向に垂直な断面において、前記間座の軸受半径方向の内側をく面は前記拡張部を含めて面一に形成し、前記拡張部から前記間座の軸受半径方向の外側を向く面に向けて同一の勾配でかつ面一の斜面部を形成し、
前記間座の、軸受半径方向の内側または外側を向く面にただ一つのゲートを設けることにより、樹脂の流動方向を間座ところとの接触線方向に対して直交させたことを特徴とするころ軸受。
In a roller bearing having a plurality of rollers movably interposed between an inner ring raceway surface and an outer ring raceway surface, and a spacer between adjacent rollers,
The spacer is a plate formed integrally by synthetic resin injection molding, has a roller contact surface that contacts the roller rolling surface on both sides, and both ends in the longitudinal direction extend in the circumferential direction. An extension with a surface facing the roller end face is formed,
In a cross section perpendicular to the bearing circumferential direction of the spacer, the inner side of the bearing radial direction of the spacer toward Ku surface is formed flush, including the extension, the bearing of the spacer from the extended portion Forming the same slope and the same slope toward the radially outward surface,
Rollers characterized in that the flow direction of the resin is orthogonal to the contact line direction with the spacer by providing a single gate on the surface of the spacer facing the inner or outer side in the bearing radial direction. bearing.
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ころと、隣り合うころ間に間座を具備するころ軸受において、
前記間座が合成樹脂の射出成形により一体的に形成された板状で、両面にころの転動面と接触するころ接触面を有し、かつ、長手方向の両端を円周方向に拡張してころ端面と向き合う面をもった拡張部が形成してあり、
前記間座の軸受円周方向に垂直な断面において、前記間座の軸受半径方向の外側を向く面は前記拡張部を含めて面一に形成し、前記拡張部から前記間座の軸受半径方向の内側を向く面に向けて同一の勾配でかつ面一の斜面部を形成し、
前記間座の、軸受半径方向の内側または外側を向く面にただ一つのゲートを設けることにより、樹脂の流動方向を間座ところとの接触線方向に対して直交させたことを特徴とするころ軸受。
In a roller bearing having a plurality of rollers movably interposed between an inner ring raceway surface and an outer ring raceway surface, and a spacer between adjacent rollers,
The spacer is a plate formed integrally by synthetic resin injection molding, has a roller contact surface that contacts the roller rolling surface on both sides, and both ends in the longitudinal direction extend in the circumferential direction. An extension with a surface facing the roller end face is formed,
In the cross section perpendicular to the bearing circumferential direction of the spacer, a surface of the spacer facing outward in the bearing radial direction is formed to be flush with the extended portion, and from the extended portion to the bearing radial direction of the spacer. Forming the same slope and the same slope toward the inside facing surface,
Rollers characterized in that the flow direction of the resin is orthogonal to the contact line direction with the spacer by providing a single gate on the surface of the spacer facing the inner or outer side in the bearing radial direction. bearing.
前記間座の長手方向の中央部で軸受半径方向の内側または外側を向く面に切欠き部を設けた請求項1または2のころ軸受。 The roller bearing according to claim 1 or 2, wherein a notch portion is provided on a surface facing the inner side or the outer side in the radial direction of the bearing at a central portion in the longitudinal direction of the spacer . 円周方向すきまをS、ころ長さをLw、前記間座の拡張部長さの最大値をLとしたとき、間座の拡張部ところ端面の間のすきまSaが式1の範囲内である請求項1、2または3のころ軸受。When the circumferential clearance is S, the roller length is Lw, and the maximum length of the extended portion of the spacer is L, the clearance Sa between the extended portion and the end surface of the spacer is within the range of Formula 1. Item 1, 2 or 3 roller bearing.
Figure 0004708222
Figure 0004708222
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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPH09242759A (en) * 1996-03-11 1997-09-16 Nippon Seiko Kk Roller bearing
JP2001193740A (en) * 2000-01-13 2001-07-17 Nsk Ltd Retaining piece and linear motion device equipped with the piece
JP2003194058A (en) * 2001-12-27 2003-07-09 Nsk Ltd Rectilinear device
JP2003239964A (en) * 2002-02-19 2003-08-27 Nsk Ltd Linear motion device
JP2005003178A (en) * 2003-06-16 2005-01-06 Koyo Seiko Co Ltd Rolling bearing and separator used for the same
JP2005090712A (en) * 2003-09-19 2005-04-07 Koyo Seiko Co Ltd Rolling bearing and separator for rolling bearing

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPH09242759A (en) * 1996-03-11 1997-09-16 Nippon Seiko Kk Roller bearing
JP2001193740A (en) * 2000-01-13 2001-07-17 Nsk Ltd Retaining piece and linear motion device equipped with the piece
JP2003194058A (en) * 2001-12-27 2003-07-09 Nsk Ltd Rectilinear device
JP2003239964A (en) * 2002-02-19 2003-08-27 Nsk Ltd Linear motion device
JP2005003178A (en) * 2003-06-16 2005-01-06 Koyo Seiko Co Ltd Rolling bearing and separator used for the same
JP2005090712A (en) * 2003-09-19 2005-04-07 Koyo Seiko Co Ltd Rolling bearing and separator for rolling bearing

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