JP2012072864A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
JP2012072864A
JP2012072864A JP2010219181A JP2010219181A JP2012072864A JP 2012072864 A JP2012072864 A JP 2012072864A JP 2010219181 A JP2010219181 A JP 2010219181A JP 2010219181 A JP2010219181 A JP 2010219181A JP 2012072864 A JP2012072864 A JP 2012072864A
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Prior art keywords
bearing
rolling
rolling bearing
cage
ball
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JP5724275B2 (en
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Yoshiaki Katsuno
美昭 勝野
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NSK Ltd
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NSK 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/46—Gap sizes or clearances

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

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing that can suppress irregular pitches of rollers in the circumferential direction, and can minimally suppress a centrifugal whirl of an axis of rotation.SOLUTION: The rolling bearing 10 includes: an inner ring 11 having an inner ring raceway surface 11a at its external peripheral surface; an outer ring 12 having an outer ring raceway surface 12a at its internal periphery face; a plurality of the rollers 13 which are rollingly arranged between the inner ring raceway surface 11a and the outer ring raceway surface 12a; and a synthetic resin cage 15 in which cut parts 14 are formed at least at one portion in the circumferential direction, and which holds the plurality of rollers 13 at almost equal intervals in the circumferential direction. Then, the rollers 13 are also inserted into a clearance between the cut parts 14.

Description

本発明は、例えば、産業機械、ロボットの関節部や旋回機構部、工作機械の主軸、回転テーブルや主軸旋回機構部、医療機器、半導体／液晶製造装置、光学及びオプトエレクトロニクス装置等の回転支持部に用いられる転がり軸受に関する。 The present invention includes, for example, industrial machinery, robot joints and turning mechanisms, spindles of machine tools, rotary tables and spindle turning mechanisms, medical equipment, semiconductor / liquid crystal manufacturing apparatuses, optical and optoelectronic devices, and the like. The present invention relates to a rolling bearing used in the above.

従来の転がり軸受として、図９に示すように、円周方向の一ヶ所に切断部を設けた合成樹脂製の冠形保持器が提案されている（例えば、特許文献１及び２参照）。特許文献１に記載の転がり軸受では、切断部を設けることで、内外輪及び玉と保持器との熱膨張係数の違い等により玉とポケットとの間に発生する突っ張り力を緩和して保持器の摩耗等を防止することが記載されている。   As a conventional rolling bearing, as shown in FIG. 9, a synthetic resin crown-shaped cage provided with a cutting portion at one place in the circumferential direction has been proposed (see, for example, Patent Documents 1 and 2). In the rolling bearing described in Patent Document 1, by providing a cutting portion, the tension force generated between the ball and the pocket due to the difference in thermal expansion coefficient between the inner and outer rings and the ball and the cage is alleviated. It is described that the wear and the like are prevented.

また、特許文献２に記載の転がり軸受では、円周方向の一ヶ所に切断部が設けられるとともに、切断部の円周方向幅を温度変化と吸水率変化による保持器の伸長分とし、軌道輪との案内すきまを確保することが記載されている。   Further, in the rolling bearing described in Patent Document 2, a cutting part is provided at one place in the circumferential direction, and the circumferential width of the cutting part is set as an extension of the cage due to a change in temperature and a change in water absorption rate. It is described to secure a guide clearance.

ところで、特許文献１に記載の転がり軸受では、玉案内方式を採用して、玉とポケットとの間の半径方向すきまは小さく設定されているので、軸受の回転による昇温で、軸受各部品（例えば、内輪、外輪及び玉が軸受鋼、保持器がポリアミド樹脂などの合成樹脂で形成されている場合）間の線膨張係数の差により保持器が相対的に膨張する際に、半径方向には膨張しにくく、相対膨張分は円周方向に向かう。   By the way, in the rolling bearing described in Patent Document 1, the ball guide method is adopted, and the radial clearance between the ball and the pocket is set to be small. (For example, when the inner ring, outer ring and ball are made of bearing steel, and the cage is made of synthetic resin such as polyamide resin) It is difficult to expand, and the relative expansion is directed in the circumferential direction.

その結果、保持器の切断部の円周方向すきまが小さくなり、使用環境温度も含めて軸受の昇温値が高い場合、保持器の切断部の円周方向の端面同士が突っ張り干渉して、該干渉部での発熱や摩耗、損傷が生じるという問題がある。また、保持器がポリアミド樹脂などの一般的な汎用合成樹脂で形成されている場合は、空気中の水分を吸収して膨張することもあり、吸水による膨張量が加わることも問題である。   As a result, the clearance in the circumferential direction of the cutting part of the cage is reduced, and if the temperature rise value of the bearing is high, including the operating environment temperature, the circumferential end surfaces of the cutting part of the cage are stretched and interfered, There is a problem that heat generation, wear, and damage occur in the interference portion. In addition, when the cage is formed of a general general-purpose synthetic resin such as a polyamide resin, the cage may expand by absorbing moisture in the air, and the amount of expansion due to water absorption is also a problem.

また、特許文献２に記載の転がり軸受では、切断部の円周方向幅を温度変化と吸水率変化による保持器の伸長分（温度膨張＋吸水膨張）としているが、切断部の円周方向幅が広くなりすぎてしまい、温度上昇が小さい条件や乾燥した雰囲気条件では、切断部の円周方向幅の変化が小さく、切断部を挟んだ部分での玉間の円周方向の距離が他の玉間の円周方向距離より大きくなり、玉の円周方向の不等配が発生する。   Further, in the rolling bearing described in Patent Document 2, the circumferential width of the cut portion is defined as the extension of the cage (temperature expansion + water absorption expansion) due to temperature change and water absorption change. However, under conditions where the temperature rise is small or the atmosphere is dry, the change in the circumferential width of the cut part is small, and the circumferential distance between the balls at the part across the cut part is It becomes larger than the circumferential distance between the balls, and uneven distribution in the circumferential direction of the balls occurs.

玉の円周方向の不等配が生じると、軸受の径方向の剛性が円周位相で不均一（玉の円周方向の不等配部の位相で剛性低下）になるため、軸受回転時に玉の公転周期に対応した振れ回り、いわゆるＮＲＲＯ値（内輪２回転に約１回の周期）が増加する。特に、回転精度が要求される工作機械の主軸、回転テーブル及び主軸の旋回機構部などの回転支持部に本軸受を使用した場合、回転軸の振れ回りが大きくなり（ＮＲＲＯ値が大）、フライス加工などでは加工面に縞模様が発生したり、旋盤加工などでは加工面の引き目不良や真円度悪化などが発生したりするという問題がある。   If the balls are not evenly distributed in the circumferential direction, the radial rigidity of the bearing will be non-uniform in the circumferential phase (decrease in rigidity due to the phase of the unevenly distributed portion of the ball in the circumferential direction). A swing corresponding to the revolution period of the ball, a so-called NRRO value (a cycle of about once per two rotations of the inner ring) increases. In particular, when this bearing is used in a rotation support part such as a spindle of a machine tool, a rotary table, and a turning mechanism part of the spindle that require rotational accuracy, the rotation of the rotary shaft becomes large (NRRO value is large), and milling There is a problem that a striped pattern is generated on the processed surface in machining, and a stitching defect on the processed surface or a deterioration in roundness occurs in lathe processing.

特開２００３−３３６６４０号公報JP 2003-336640 A 特開２００６−２２６４９６号公報JP 2006-226696 A

本発明は、このような不都合を解消するためになされたものであり、その目的は、転動体の円周方向の不等配を抑制して、回転軸の振れ回りを小さく抑えることができる転がり軸受を提供することにある。   The present invention has been made in order to eliminate such inconveniences, and the object of the present invention is to reduce rolling around the rotating shaft by suppressing the uneven distribution of the rolling elements in the circumferential direction. It is to provide a bearing.

上記目的を達成するために、請求項１に係る転がり軸受は、外周面に内輪軌道面を有する内輪と、内周面に外輪軌道面を有する外輪と、前記内輪軌道面と前記外輪軌道面との間に転動自在に設けられた複数の転動体と、円周方向の少なくとも一カ所に切断部が形成され、前記複数の転動体を円周方向に略等間隔で保持する合成樹脂製の保持器と、を備え、前記切断部の相対する切断面の間に前記転動体を挿入したことを特徴としている。   In order to achieve the above object, a rolling bearing according to claim 1 includes an inner ring having an inner ring raceway surface on an outer peripheral surface, an outer ring having an outer ring raceway surface on an inner peripheral surface, the inner ring raceway surface, and the outer ring raceway surface. And a plurality of rolling elements provided so as to freely roll between, and a cutting portion is formed in at least one place in the circumferential direction, and the plurality of rolling elements are made of a synthetic resin that holds the rolling elements at substantially equal intervals in the circumferential direction. A rolling cage, wherein the rolling element is inserted between the opposing cutting surfaces of the cutting portion.

また、請求項２に係る転がり軸受は、請求項１に係る発明において、前記切断面の少なくとも一方に、潤滑剤を溜めるための凹溝部を設けたことを特徴としている。   A rolling bearing according to claim 2 is characterized in that, in the invention according to claim 1, a groove portion for storing a lubricant is provided on at least one of the cut surfaces.

さらに、請求項３に係る転がり軸受は、請求項１又は２に係る発明において、前記転動体が、玉であることを特徴としている。   Furthermore, the rolling bearing according to claim 3 is characterized in that, in the invention according to claim 1 or 2, the rolling element is a ball.

さらにまた、請求項４に係る転がり軸受は、請求項１又は２に係る発明において、前記転動体が、円筒ころであることを特徴としている。   Furthermore, the rolling bearing according to claim 4 is characterized in that, in the invention according to claim 1 or 2, the rolling element is a cylindrical roller.

本発明の転がり軸受によれば、転動体の円周方向の不等配を抑制して、回転軸の振れ回りを小さく抑えることができ、安定した回転性能を得ることができる。   According to the rolling bearing of the present invention, it is possible to suppress the uneven distribution in the circumferential direction of the rolling elements, to suppress the whirling of the rotating shaft, and to obtain stable rotational performance.

本発明の第１実施形態に係る転がり軸受を説明するための要部断面図である。It is principal part sectional drawing for demonstrating the rolling bearing which concerns on 1st Embodiment of this invention. 図１に示す転がり軸受に組み込まれた冠形保持器の断面図である。FIG. 2 is a cross-sectional view of a crown-shaped cage incorporated in the rolling bearing shown in FIG. 1. 図１に示す転がり軸受に組み込まれた冠形保持器の部分的斜視図である。FIG. 2 is a partial perspective view of a crown cage incorporated in the rolling bearing shown in FIG. 1. 図２の矢印Ｂ方向から見た一部を破断した図である。It is the figure which fractured | ruptured the part seen from the arrow B direction of FIG. 図１に示す転がり軸受に組み込まれた冠形保持器と転動体の構成を説明するための要部断面図である。It is principal part sectional drawing for demonstrating the structure of the crown-shaped holder | retainer integrated in the rolling bearing shown in FIG. 1, and a rolling element. 本発明品と従来品とのＮＲＲＯを示すグラフ図である。It is a graph which shows NRRO of this invention product and a conventional product. 本発明の第２実施形態に係る転がり軸受に組み込まれた冠形保持器と転動体の構成を説明するための要部断面図である。It is principal part sectional drawing for demonstrating the structure of the crown-shaped holder | retainer integrated in the rolling bearing which concerns on 2nd Embodiment of this invention, and a rolling element. 本発明の第３実施形態に係る転がり軸受に組み込まれた冠形保持器と転動体の構成を説明するための要部断面図である。It is principal part sectional drawing for demonstrating the structure of the crown-shaped holder | retainer integrated in the rolling bearing which concerns on 3rd Embodiment of this invention, and a rolling element. 従来の保持器を軸方向から見た要部断面図である。It is principal part sectional drawing which looked at the conventional cage | basket from the axial direction.

以下、本発明の実施の形態を図を参照して説明する。図１は本発明の第１の実施の形態を示す単列玉軸受を２列組み合わせた状態を示す要部断面図、図２は玉案内保持器を示す断面図、図３は保持器を径方向内側から見た部分斜視図、図４は図２の矢印Ｂ方向から見た矢視図、図５は図１に示す転がり軸受に組み込まれた冠形保持器と転動体の構成を説明するための要部断面図、図７は本発明の第２実施形態に係る転がり軸受に組み込まれた冠形保持器と転動体の構成を説明するための要部断面図、図８は本発明の第３実施形態に係る転がり軸受に組み込まれた冠形保持器と転動体の構成を説明するための要部断面図である。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of an essential part showing a state in which two rows of single-row ball bearings according to the first embodiment of the present invention are combined, FIG. 2 is a cross-sectional view showing a ball guide cage, and FIG. 4 is a partial perspective view as seen from the inner side in the direction, FIG. 4 is an arrow view as seen from the direction of arrow B in FIG. 2, and FIG. 5 illustrates the configuration of the crown-shaped cage and rolling elements incorporated in the rolling bearing shown in FIG. FIG. 7 is a cross-sectional view of a main part for explaining the configuration of a crown-shaped cage and rolling elements incorporated in a rolling bearing according to a second embodiment of the present invention, and FIG. It is principal part sectional drawing for demonstrating the structure of the crown-shaped cage | basket incorporated in the rolling bearing which concerns on 3rd Embodiment, and a rolling element.

図１に示すように、本実施形態の転がり軸受１０（以下、幅狭玉軸受１０とも称す）は、アンギュラ玉軸受とされており、２列のアンギュラ玉軸受を背面組合せ（接触角がハの字となる配列）としている。各転がり軸受１０は、外周面に内輪軌道面１１ａを有する内輪１１と、内周面に外輪軌道面１２ａを有する外輪１２と、内輪軌道面１１ａと外輪軌道面１２ａとの間に転動自在に設けられた複数の玉（転動体）１３と、円周方向の一カ所に切断部１４（図５参照）が形成され、複数の玉１３を円周方向に略等間隔で保持する合成樹脂製の冠形保持器１５と、を備える。また、２列の幅狭玉軸受１０の各外輪１２の軸方向外側の端部内周面には、それぞれ非接触型のシール部材１６が装着されている。なお、シール部材１６は、接触型タイプでもよく、また、材料、形状は特に限定されない。   As shown in FIG. 1, a rolling bearing 10 (hereinafter also referred to as a narrow ball bearing 10) of this embodiment is an angular ball bearing, and two rows of angular ball bearings are combined in the back (contact angle is C). Array). Each rolling bearing 10 is freely rollable between an inner ring 11 having an inner ring raceway surface 11a on an outer peripheral surface, an outer ring 12 having an outer ring raceway surface 12a on an inner peripheral surface, and an inner ring raceway surface 11a and an outer ring raceway surface 12a. A plurality of balls (rolling elements) 13 provided, and a cutting portion 14 (see FIG. 5) is formed at one place in the circumferential direction, and the plurality of balls 13 is made of a synthetic resin that holds the balls 13 in the circumferential direction at substantially equal intervals. The crown-shaped cage 15 is provided. Further, non-contact type seal members 16 are mounted on the inner peripheral surfaces of the outer ends of the outer rings 12 of the two rows of narrow ball bearings 10 in the axial direction. The seal member 16 may be a contact type, and the material and shape are not particularly limited.

ここで、本実施形態では、軸方向の省スペース化を図るため、転がり軸受１０の軸方向断面幅Ｂと半径方向断面高さＨ（＝（外輪外径Ｄ−内輪内径ｄ）／２）との断面寸法比（Ｂ／Ｈ）をＢ／Ｈ＜０．６３としている。   In this embodiment, in order to save space in the axial direction, the axial sectional width B and the radial sectional height H of the rolling bearing 10 (= (outer ring outer diameter D−inner ring inner diameter d) / 2) and The cross-sectional dimension ratio (B / H) is set to B / H <0.63.

なお、Ｂ／Ｈは、理論的にはＢ／Ｈ＞０であるが、現実的には、使用する玉径や保持器、シール部材の設計、選定等を加味すると、Ｂ／Ｈ＞０．１０、好ましくはＢ／Ｈ＞０．２０、より好ましくはＢ／Ｈ＞０．３０とする。   B / H is theoretically B / H> 0, but in reality, considering the design, selection, etc. of the ball diameter, cage, and seal member to be used, B / H> 0. 10, preferably B / H> 0.20, more preferably B / H> 0.30.

また、国際標準化機構（ＩＳＯ）で規定されている標準寸法玉軸受の場合、Ｂ／Ｈが１．０前後のものが多くを占める。したがって、Ｂ／Ｈ＜０．５に設定すれば、標準玉軸受約１列分の幅方向スペースで２列分の幅狭玉軸受１０を配設させることができ、省スペース化が図れる。   Further, in the case of standard size ball bearings defined by the International Organization for Standardization (ISO), those with a B / H of around 1.0 account for the majority. Therefore, if B / H <0.5 is set, the narrow ball bearings 10 for two rows can be disposed in the width direction space for about one row of standard ball bearings, and space saving can be achieved.

また、アンギュラ玉軸受の場合、１列では一方向の軸方向荷重しか受けられず、また、モーメント荷重を受けることはできないが、２列以上組合わせることで、両方向の軸方向荷重やモーメント荷重の負荷が可能となる。また、予圧を付加することもできるので、省スペース化と共にラジアル剛性やアキシャル剛性及びモーメント剛性なども大きくすることができる。   In the case of angular contact ball bearings, only one axial load can be received in one row and moment load cannot be received. However, by combining two or more rows, the axial load and moment load in both directions can be reduced. Load becomes possible. In addition, since preload can be applied, it is possible to save space and increase radial rigidity, axial rigidity, moment rigidity, and the like.

また、Ｂ／Ｈ＜０．２５に設定すれば、さらなる省スペース化と共に、標準玉軸受約１列分の幅方向スペースで４列の幅狭玉軸受を配設させることができ、さらに剛性の向上が可能である。   Moreover, if B / H <0.25, it is possible to arrange four rows of narrow ball bearings in a space in the width direction of about one row of standard ball bearings with further space saving, and further increase rigidity. Improvement is possible.

また、（Ｂ／Ｈ）＝０．６３未満とすることで、軸やハウジングに軸受を組み込んだ場合（特に、軸やハウジングとすきま嵌合で組み込んだ場合）、外輪を端面押え、内輪を軸受ナット等でそれぞれ固定した場合の内外輪の変形（特に真円度の悪化）を抑制することができると共に、変形によって生じるトルク不良や回転精度不良、あるいは、発熱増大、摩耗や焼付き等の不具合を防止することができる。   Also, by setting (B / H) to less than 0.63, when the bearing is incorporated in the shaft or housing (especially when it is assembled by clearance fitting with the shaft or housing), the outer ring is pressed against the end face, and the inner ring is the bearing. It is possible to suppress deformation of the inner and outer rings (especially worsening of roundness) when they are fixed with nuts, etc., as well as torque failure and rotation accuracy caused by deformation, or problems such as increased heat generation, wear and seizure. Can be prevented.

さらに、（Ｂ／Ｈ）＝０．６３未満とすることで、軸受の幅寸法が従来の標準単列玉軸受の約半分となるので、玉径も従来の玉軸受の半分程度となるが、逆に１列あたりの玉数が少なくとも２倍以上に増加し、軸受剛性は従来の玉軸受に対して増加する。   Furthermore, by setting (B / H) to less than 0.63, the width of the bearing is about half that of a conventional standard single-row ball bearing, so the ball diameter is also about half that of a conventional ball bearing. Conversely, the number of balls per row increases at least twice, and the bearing stiffness increases compared to conventional ball bearings.

また、国際標準化機構（ＩＳＯ）で規定されている寸法系列が１８（例えば、６８２０）、１９（例えば、６９３８）、１０（例えば、７０１６Ａ）、０２（例えば、７２２４Ｃ）、０３（例えば、７３５０Ａ）などの標準寸法玉軸受では、軸受内径寸法がφ５ｍｍ〜φ５００ｍｍにおいては、断面寸法比（Ｂ／Ｈ）はＢ／Ｈ＝０．６３〜１．１７となっているが、本実施形態の幅狭玉軸受１０は、軸方向に幅狭としたので、上述の断面寸法比に該当しないものとなる。   The dimension series defined by the International Organization for Standardization (ISO) is 18 (for example, 6820), 19 (for example, 6938), 10 (for example, 7016A), 02 (for example, 7224C), 03 (for example, 7350A). In the case of standard size ball bearings such as the above, when the inner diameter of the bearing is φ5 mm to φ500 mm, the cross-sectional dimension ratio (B / H) is B / H = 0.63 to 1.17. Since the ball bearing 10 is narrow in the axial direction, it does not correspond to the above-described cross-sectional dimension ratio.

本実施形態の幅狭玉軸受１０では、軸受の負荷容量や剛性を上げるために、円周方向に隣り合う玉１３間のピッチは極力小さくし、できる限り玉数を多くしている。通常の玉軸受では、玉数は多くとも３０〜４０個以下／１列程度であるが、本実施形態では、５０個以上、好ましくは６０個以上、より好ましくは７０個以上／１列としている。   In the narrow ball bearing 10 of this embodiment, in order to increase the load capacity and rigidity of the bearing, the pitch between the balls 13 adjacent in the circumferential direction is made as small as possible, and the number of balls is increased as much as possible. In a normal ball bearing, the number of balls is at most about 30 to 40 or less per row, but in this embodiment, 50 or more, preferably 60 or more, more preferably 70 or more per row. .

アンギュラ玉軸受の場合、接触角は、大きなモーメント荷重を負荷した際に、内外輪みぞ肩部への玉と内外輪みぞ接触部の乗り上げを抑えるため、概ね６０°以下、望ましくは５０°以下、さらに望ましくは４０°以下がよいが、２０°未満の場合は、許容アキシャル荷重やモーメント剛性が低下するので好ましくない。本実施形態における適正な玉径は、シール部材等の装着有無により変化するが、剛性を増加させるため、極端に玉径を小さくすると、玉と内外輪の軌道みぞとの接触部間の面圧が増加し、耐圧痕性が低下するおそれがあるため、概ね、軸受幅（Ｂ）の３０〜９０％が望ましい。   In the case of an angular contact ball bearing, the contact angle is approximately 60 ° or less, preferably 50 ° or less in order to suppress the ball and the inner / outer ring groove contact portion from riding on the shoulder portion of the inner / outer ring groove when a large moment load is applied. More preferably, it is 40 ° or less, but if it is less than 20 °, the allowable axial load and moment rigidity are lowered, which is not preferable. The appropriate ball diameter in the present embodiment varies depending on whether or not a seal member or the like is mounted. However, in order to increase rigidity, if the ball diameter is extremely reduced, the surface pressure between the contact portions between the balls and the track grooves of the inner and outer rings is reduced. In general, the pressure resistance is likely to be reduced, so that generally 30 to 90% of the bearing width (B) is desirable.

更に、本実施形態では、玉１３の軸方向ピッチをできるだけ組合せ側端面の反対側にずらし（図１：Ｘ１＞Ｘ２）、保持器１５のリング部１７（図２〜図５参照）が軸受組合せ端面側になるように配置しており、リング部１７の軸方向肉厚を大きくし、また、モーメント剛性を上げるための作用点間距離を大きくとれるようにしている。 Furthermore, in this embodiment, the axial pitch of the balls 13 is shifted as much as possible to the side opposite to the combination side end face (FIG. 1: X 1 > X 2 ), and the ring portion 17 (see FIGS. 2 to 5) of the cage 15 is provided. It is arranged so as to be on the bearing combination end face side, so that the axial thickness of the ring portion 17 is increased, and the distance between operating points for increasing moment rigidity can be increased.

また、軸受の材料としては、標準の軸受鋼（ＳＵＪ２やＳＵＪ３）など、特に限定されないが、必要に応じて、これらの材料で、軸受の寸法安定性や耐摩耗性などの機械的性質を向上させるために、内輪１１及び外輪１２の少なくとも一方に、サブゼロ処理を施してもよい。   In addition, the bearing material is not particularly limited, such as standard bearing steel (SUJ2 or SUJ3), but if necessary, these materials improve mechanical properties such as dimensional stability and wear resistance of the bearing. In order to achieve this, sub-zero processing may be performed on at least one of the inner ring 11 and the outer ring 12.

サブゼロ処理の方法としては、例えば、焼入れ直後に、液体窒素を用いて−１５０°Ｃ程度の雰囲気とし、本サブゼロ処理後に焼戻しを行なう。そして、サブゼロ処理と焼戻し処理とを数回繰り返す。冷却溶媒として、液体窒素使用のサブゼロ処理では、繰り返し回数は多くとも３回程度でかまわない。サブゼロ処理によって、組織中の残留オーステナイト（γＲ）がマルテンサイトに変態する。併せて、結晶粒の安定化も促進されるので、これにより経時寸法変化の防止と耐摩耗性などの機械的性質が向上する。   As a sub-zero treatment method, for example, immediately after quenching, an atmosphere of about −150 ° C. is formed using liquid nitrogen, and tempering is performed after the sub-zero treatment. Then, the sub-zero process and the tempering process are repeated several times. In the sub-zero treatment using liquid nitrogen as the cooling solvent, the number of repetitions may be at most about 3. Residual austenite (γR) in the structure is transformed into martensite by the sub-zero treatment. In addition, since the stabilization of the crystal grains is promoted, this improves the mechanical properties such as prevention of dimensional change with time and wear resistance.

本実施形態の場合、内輪１１及び外輪１２の軸方向幅が狭いので、そりや真円度不良などの経時寸法変化が発生しやすい傾向がある。したがって、サブゼロ処理により、前記経時寸法変化を抑制することができ、特に、軸受精度が必要な工作機械の回転テーブルや主軸旋回機構部、印刷機械のドラム等の回転機構部などの回転支持部に本実施形態の幅狭玉軸受１０を使用する場合、軸受精度劣化による機器の精度不具合を防止でき、長期的に良好な機能を保持することができる。   In the case of the present embodiment, since the axial widths of the inner ring 11 and the outer ring 12 are narrow, there is a tendency that dimensional changes such as warpage and roundness failure tend to occur. Accordingly, the sub-zero treatment can suppress the dimensional change with time, and in particular, in rotation support parts such as a rotary table of a machine tool, a spindle turning mechanism part, and a rotary mechanism part such as a drum of a printing machine that require bearing accuracy. When the narrow ball bearing 10 of the present embodiment is used, it is possible to prevent malfunctions of the equipment due to deterioration of the bearing accuracy, and it is possible to maintain a good function in the long term.

また、例えば真空用途や腐食環境などでは、軸受鋼以外に、耐食材料であるステンレス鋼系材料（例えば、ＳＵＳ４４０Ｃ等のマルテンサイト系ステンレス鋼材料やＳＵＳ３０４等のオーステナイト系ステンレス鋼材料、ＳＵＳ６３０等の析出硬化系ステンレス鋼材料など）、チタン合金やセラミック系材料（例えば、Ｓｉ3 Ｎ4 ，ＳｉＣ，Ａｌ2
Ｏ3 ，ＺｒＯ2など）を採用してもよい。 For example, in vacuum applications and corrosive environments, in addition to bearing steel, stainless steel materials that are corrosion resistant materials (for example, martensitic stainless steel materials such as SUS440C, austenitic stainless steel materials such as SUS304, precipitation of SUS630, etc.) Hardened stainless steel materials), titanium alloys and ceramic materials (eg, Si 3 N 4 , SiC, Al 2)
O 3 , ZrO 2, etc.) may be employed.

潤滑方法も特に限定されず、一般的な使用環境では、鉱油系グリースや合成油系（例えば、リチウム系、ウレア系等）のグリースや油を使用でき、真空用途などでは、フッ素系のグリースまたは油、あるいはフッ素樹脂、ＭＯＳ2 などの固体潤滑剤を使用することができる。 The lubrication method is not particularly limited, and mineral oil grease or synthetic oil grease (for example, lithium or urea) or oil can be used in a general usage environment. Oil, or a solid lubricant such as fluororesin or MOS 2 can be used.

玉案内保持器１５は、図２〜図４に示すように、リング部１７と、このリング部１７の一端部に周方向に略等間隔で複数箇所軸方向に突設された柱部１８と、各柱部１８間に形成されて玉１３を周方向に転動可能に保持する多数のポケット部１９と、このポケット部１９のリング部１７とは反対側の先端部に形成された玉１３の抜け出しを防止する一対の玉係止部とを備えた柔軟性のある冠形保持器の構成を有する。この保持器１５の材料は、例えば、ポリアミド、ポリアセタール、ポリフェニレンサルファイド等の合成樹脂材とし、必要に応じて、合成樹脂材にガラス繊維や炭素繊維等の補強材を混入した材料を用いる。   As shown in FIGS. 2 to 4, the ball guide retainer 15 includes a ring portion 17, and column portions 18 projecting in a plurality of axial directions at substantially equal intervals in the circumferential direction on one end portion of the ring portion 17. A large number of pockets 19 formed between the pillars 18 to hold the balls 13 so as to roll in the circumferential direction, and the balls 13 formed at the tip of the pockets 19 on the side opposite to the ring parts 17. And a pair of ball locking portions that prevent the slipping out of the flexible crown-shaped cage. The material of the cage 15 is, for example, a synthetic resin material such as polyamide, polyacetal, or polyphenylene sulfide, and a material in which a reinforcing material such as glass fiber or carbon fiber is mixed into the synthetic resin material is used as necessary.

また、保持器１５は、図５に示すように、リング部１７の少なくとも円周方向の一箇所で互いに隣り合うポケット部１９間を予め切断して切断部１４を形成し、切断部１４の相対する切断面の間に転動体１３を挿入したうえ、転動体１３と切断面間に所定のすき間ΔＬ／２を持たせた構造としている（ΔＬ：軸受の温度上昇や保持器の吸水を考慮した切断部１４の最適すき間）。   Further, as shown in FIG. 5, the retainer 15 forms a cut portion 14 by cutting in advance between the pocket portions 19 adjacent to each other at least at one place in the circumferential direction of the ring portion 17. In addition, the rolling element 13 is inserted between the cut surfaces, and a predetermined clearance ΔL / 2 is provided between the rolling element 13 and the cut surface (ΔL: taking into account the temperature rise of the bearing and the water absorption of the cage) Optimum clearance of the cutting part 14).

本実施形態のような幅狭玉軸受１０では、冠型保持器１５の円周方向に切断部１４を形成し、さらに、相対する切断面の間に転動体１３を挿入したことで、以下のような効果を奏する。   In the narrow ball bearing 10 as in the present embodiment, the cutting portion 14 is formed in the circumferential direction of the crown-shaped cage 15, and the rolling elements 13 are inserted between the opposing cutting surfaces, so that the following The effect is produced.

即ち、従来の転動体１３を挿入しない場合では、図９に示すように、切断部１４における転動体１３間の距離は（ΔＬ＋２・ΔＳ）となる一方（ΔＳ：保持器１５の柱部１８の強度を考慮した必要最小肉厚）、切断部１４の相対する切断面の間に転動体１３を挿入する場合では、図５に示すように、転動体１３間の距離は（ΔＬ／２＋ΔＳ）となる。つまり、切断部１４に転動体１３を挿入する本実施形態では、切断部１４に転動体１３を挿入しない場合に比べ、転動体１３の不等配を約１／２にすることができる。よって、上述のように転動体１３の不等配によって発生する玉の公転周期（保持器の回転周期）ごとの回転振れ（ＮＲＲＯ）の増加を大幅に抑制することが可能となる。   That is, in the case where the conventional rolling element 13 is not inserted, as shown in FIG. 9, the distance between the rolling elements 13 in the cutting portion 14 is (ΔL + 2 · ΔS) (ΔS: of the column portion 18 of the retainer 15). In the case where the rolling elements 13 are inserted between the opposing cut surfaces of the cutting portion 14, the distance between the rolling elements 13 is (ΔL / 2 + ΔS) as shown in FIG. Become. That is, in the present embodiment in which the rolling elements 13 are inserted into the cutting part 14, the unequal distribution of the rolling elements 13 can be reduced to about ½ compared to the case where the rolling elements 13 are not inserted into the cutting part 14. Therefore, as described above, it is possible to significantly suppress an increase in rotational runout (NRRO) for each ball revolution period (rotation period of the cage) generated by uneven distribution of the rolling elements 13.

ここで、図６は、本発明品と従来品とのＮＲＲＯを示すグラフ図である。本発明品と従来品は、それぞれ２列背面組合せアンギュラ軸受（軸受内径：φ１７０ｍｍ、軸受外径：φ２１５ｍｍ、軸受幅：
１３．５ｍｍ、接触角：３５°、玉径：６．３５ｍｍ、玉数：８０個、玉ピッチ円径：φ１９２．５（Ｂ／Ｈ＝０．６０）、内輪・外輪及び玉の材料を軸受鋼（ＳＵＪ２、線膨張係数：１２．５×１０−６（Ｋ−１））を基本とし、冠形保持器（玉案内方式、ポリアミド６６、強化材混入なし、線膨張係数：８０×１０−６（Ｋ−１））の構成のみを変更させた場合の、本発明品と従来品のＮＲＲＯを比較した結果を示している。 Here, FIG. 6 is a graph showing the NRRO between the product of the present invention and the conventional product. The product of the present invention and the conventional product are each a two-row back side combined angular bearing (bearing inner diameter: φ170 mm, bearing outer diameter: φ215 mm, bearing width:
13.5 mm, contact angle: 35 °, ball diameter: 6.35 mm, number of balls: 80 balls, ball pitch circle diameter: φ192.5 (B / H = 0.60), bearing inner / outer ring and ball material Based on steel (SUJ2, linear expansion coefficient: 12.5 × 10 −6 (K −1 )), crown-shaped cage (ball guide system, polyamide 66, no reinforcing material mixed, linear expansion coefficient: 80 × 10 − 6 shows a result of comparing the NRRO of the product of the present invention and the conventional product when only the configuration of 6 (K −1 ) is changed.

図６の結果より、本発明品のＮＲＲＯは、従来品に比べて約１／２に減少していることがわかる。つまり、軸受に本発明の構成を採用することにより、転動体の不等配によって発生する玉の公転周期（保持器の回転周期）ごとの回転振れ（ＮＲＲＯ）の増加を大幅に抑制することが可能となった。   From the result of FIG. 6, it can be seen that the NRRO of the product of the present invention is reduced to about ½ compared to the conventional product. That is, by adopting the configuration of the present invention for the bearing, it is possible to greatly suppress an increase in rotational runout (NRRO) for each ball revolution cycle (rotation cycle of the cage) caused by uneven distribution of rolling elements. It has become possible.

次に、図７を参照して、本発明の第２実施形態に係る転がり軸受に組み込まれた保持器１５を説明する。この保持器１５では、第１実施形態の切断面に、潤滑剤を溜めるための凹溝２０ａを設けた構成としている。図７に示すように潤滑剤を保持する凹溝２０ａを設ければ、転動体１３と保持器１５の接触部における潤滑条件を向上させることが可能となる。また、凹溝２０aは転動体１３と保持器１５の接触部からずれた位置に設けることが好ましい。さらに、図７に示すように凹溝２０aを軸方向に開口する形状にすれば、射出成形で保持器１５を製造する場合、型を軸方向に離型する方式（アキシャアルドロー方式）で型から保持器１５を取り出す際、型との干渉が無く取り出しが容易となる。なお、潤滑剤を保持する凹溝２０ａは、切断部の少なくとも一方に設ければ良い。   Next, with reference to FIG. 7, the cage 15 incorporated in the rolling bearing according to the second embodiment of the present invention will be described. The cage 15 has a configuration in which a groove 20a for storing a lubricant is provided on the cut surface of the first embodiment. As shown in FIG. 7, if the concave groove 20 a that holds the lubricant is provided, it is possible to improve the lubrication condition at the contact portion between the rolling element 13 and the cage 15. Further, it is preferable that the concave groove 20 a is provided at a position shifted from the contact portion between the rolling element 13 and the cage 15. Furthermore, if the groove 20a is shaped to open in the axial direction as shown in FIG. 7, when the cage 15 is manufactured by injection molding, the mold is released in the axial direction (axial axial draw). When the cage 15 is taken out from the mold, it can be easily taken out without interference with the mold. The concave groove 20a that holds the lubricant may be provided in at least one of the cut portions.

次に、図８を参照して、本発明の第３実施形態に係る転がり軸受に組み込まれた保持器１５を説明する。この保持器１５では、第２実施形態の切断面と同様に潤滑剤を溜めるための凹溝２０ｂを設けた構造としているが、凹溝２０ｂの形状を溝開口部より溝底部の幅を広くした構成としている。図８に示すような凹溝２０ｂ形状とすれば、保持器回転時に遠心力が作用しても潤滑剤を凹溝２０ｂ内部に保持する効果が高まり、軸受回転時における切断部１４での摩擦による発熱がさらに軽減し、摩耗や損傷を確実に防止することができる。その他の構成及び作用は、第１実施形態のものと同様である。   Next, with reference to FIG. 8, a cage 15 incorporated in a rolling bearing according to a third embodiment of the present invention will be described. The retainer 15 has a structure in which a groove 20b for storing a lubricant is provided in the same manner as the cut surface of the second embodiment, but the groove 20b has a wider groove bottom than the groove opening. It is configured. If the groove 20b has a shape as shown in FIG. 8, the effect of retaining the lubricant inside the groove 20b is enhanced even when centrifugal force is applied during rotation of the cage, and the friction at the cutting portion 14 during rotation of the bearing is increased. Heat generation is further reduced, and wear and damage can be reliably prevented. Other configurations and operations are the same as those of the first embodiment.

本発明の転がり軸受は、例えば、産業機械、ロボットの関節部や旋回機構部、工作機械の主軸、回転テーブルや主軸旋回機構部、医療機器、半導体／液晶製造装置、光学及びオプトエレクトロニクス装置等の回転支持部に好適に利用できる。   The rolling bearing of the present invention includes, for example, industrial machines, robot joints and turning mechanisms, machine tool spindles, rotary tables and spindle turning mechanisms, medical equipment, semiconductor / liquid crystal manufacturing apparatuses, optical and optoelectronic devices, etc. It can utilize suitably for a rotation support part.

１０ 転がり軸受
１１ａ 内輪軌道面
１１ 内輪
１２ａ 外輪軌道面
１２ 外輪
１３ 転動体
１４ 切断部
１５ 保持器
１６ シール部材
１７ リング部
１８ 柱部
１９ ポケット部 DESCRIPTION OF SYMBOLS 10 Rolling bearing 11a Inner ring raceway surface 11 Inner ring 12a Outer ring raceway surface 12 Outer ring 13 Rolling body 14 Cutting part 15 Cage 16 Seal member 17 Ring part 18 Column part 19 Pocket part

Claims (4)

外周面に内輪軌道面を有する内輪と、内周面に外輪軌道面を有する外輪と、前記内輪軌道面と前記外輪軌道面との間に転動自在に設けられた複数の転動体と、円周方向の少なくとも一カ所に切断部が形成され、前記複数の転動体を円周方向に略等間隔で保持する合成樹脂製の保持器と、を備えた転がり軸受において、
前記切断部の相対する切断面の間に前記転動体を挿入したことを特徴とする転がり軸受。 An inner ring having an inner ring raceway surface on an outer peripheral surface, an outer ring having an outer ring raceway surface on an inner peripheral surface, a plurality of rolling elements provided rotatably between the inner ring raceway surface and the outer ring raceway surface, In a rolling bearing comprising a cut portion formed in at least one place in the circumferential direction, and a cage made of synthetic resin that holds the plurality of rolling elements at substantially equal intervals in the circumferential direction,
A rolling bearing, wherein the rolling element is inserted between opposing cutting surfaces of the cutting portion. 前記切断面の少なくとも一方に、潤滑剤を溜めるための凹溝部を設けたことを特徴とする請求項１に記載の転がり軸受。 The rolling bearing according to claim 1, wherein a concave groove for storing a lubricant is provided on at least one of the cut surfaces. 前記転動体が、玉であることを特徴とする請求項１又は２に記載の転がり軸受。   The rolling bearing according to claim 1, wherein the rolling element is a ball. 前記転動体が、円筒ころであることを特徴とする請求項１又は２に記載の転がり軸受。   The rolling bearing according to claim 1, wherein the rolling element is a cylindrical roller.
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB869054A (en) * 1958-08-06 1961-05-25 Schaeffler Wilhelm Improvements in or relating to needle bearings
JPH02146314A (en) * 1988-11-28 1990-06-05 Nippon Seiko Kk Solid lubricating ball bearing
JP2003314559A (en) * 2002-04-18 2003-11-06 Nsk Ltd Ball bearing
JP2008261482A (en) * 2007-03-19 2008-10-30 Nsk Ltd Retainer for radial ball bearing and radial ball bearing
JP2009168108A (en) * 2008-01-15 2009-07-30 Nsk Ltd Rolling bearing
JP2009174611A (en) * 2008-01-23 2009-08-06 Toyota Motor Corp Rolling bearing

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB869054A (en) * 1958-08-06 1961-05-25 Schaeffler Wilhelm Improvements in or relating to needle bearings
JPH02146314A (en) * 1988-11-28 1990-06-05 Nippon Seiko Kk Solid lubricating ball bearing
JP2003314559A (en) * 2002-04-18 2003-11-06 Nsk Ltd Ball bearing
JP2008261482A (en) * 2007-03-19 2008-10-30 Nsk Ltd Retainer for radial ball bearing and radial ball bearing
JP2009168108A (en) * 2008-01-15 2009-07-30 Nsk Ltd Rolling bearing
JP2009174611A (en) * 2008-01-23 2009-08-06 Toyota Motor Corp Rolling bearing

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