JP2016070423A - Cage for rolling bearing - Google Patents

Cage for rolling bearing Download PDF

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JP2016070423A
JP2016070423A JP2014201921A JP2014201921A JP2016070423A JP 2016070423 A JP2016070423 A JP 2016070423A JP 2014201921 A JP2014201921 A JP 2014201921A JP 2014201921 A JP2014201921 A JP 2014201921A JP 2016070423 A JP2016070423 A JP 2016070423A
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cage
rolling
circumferential side
rolling element
rolling bearing
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JP6554772B2 (en
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健太 剱持
Kenta Kenmochi
健太 剱持
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NSK Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a cage for rolling bearing which can reduce friction generating between a rolling element and a pocket part.SOLUTION: A pocket part 20 includes a first circumferential direction side surface 11a of one column part 10, and a second circumferential direction side surface 11b of the other column part 10, out of the adjacent column parts 10. The first and second circumferential direction side surfaces 11a, 11b comprise first and second cylindrical surfaces 12a, 12b having first and second central axes Oa, Ob respectively. Circumferential direction positions of the first and second central axes Oa, Ob are not identical.SELECTED DRAWING: Figure 2

Description

本発明は転がり軸受用保持器に関する。   The present invention relates to a cage for a rolling bearing.

転がり軸受では、多くの品種において保持器が用いられる。保持器の主な役割は、回転中の各転動体を軸受に対して等配に公転させ、軸受の剛性及び回転精度を高い状態で維持することである。   In rolling bearings, cages are used in many types. The main role of the cage is to revolve each rolling element in rotation equally with respect to the bearing and maintain the rigidity and rotational accuracy of the bearing in a high state.

保持器は一般的に、転動体、内輪、及び外輪の間に、一定の隙間を介して配置される。保持器の半径方向の動き量が、内輪又は外輪で規制される場合は、内輪案内保持器又は外輪案内保持器として分類され、転動体で規制される場合は転動体案内保持器として分類される。   In general, the cage is disposed between the rolling elements, the inner ring, and the outer ring with a certain gap therebetween. When the amount of movement in the radial direction of the cage is regulated by the inner ring or the outer ring, it is classified as an inner ring guide cage or outer ring guide cage, and when it is regulated by a rolling element, it is classified as a rolling element guide cage. .

転動体の等配を維持するため、軸受回転中、保持器と転動体との間には接触が発生する。特に、転動体案内保持器の場合は、通常、保持器の動きは転動体に依存するため、保持器と転動体の接触によって発生する摩擦は大きくなる。   In order to maintain the uniform distribution of the rolling elements, contact is generated between the cage and the rolling elements during the rotation of the bearing. In particular, in the case of a rolling element guide retainer, the movement of the retainer usually depends on the rolling element, so that the friction generated by the contact between the retainer and the rolling element increases.

転動体と保持器ポケット間で発生する摩擦は、発熱や摩耗、保持器の回転不良（暴れ）を引き起こす。発熱や摩耗は軸受の劣化（寿命低下）を引き起こし、保持器の回転不良（暴れ）は回転精度不良や異常音を発生させるため、転がり軸受において、この様な摩擦の低減は解決すべき課題の一つとなっている。   Friction generated between the rolling elements and the cage pocket causes heat generation, wear, and rotation failure (rambling) of the cage. Heat generation and wear cause deterioration of the bearing (life reduction), and rotation failure of the cage (runaway) generates poor rotation accuracy and abnormal noise. Therefore, such reduction of friction in rolling bearings is a problem to be solved. It has become one.

特許文献１には、柱部の円周方向側面が、外径側凹曲面部と内径側凹曲面とを連続させてなる、ゴシックアーチ状の複合曲面からなる保持器が開示されている。これにより、ポケット内でのころの変位に拘らず、各ころの転動面と各柱部の円周方向側面の径方向端縁部とが当接（エッジ当たり）しない事を図っている。   Patent Document 1 discloses a cage having a Gothic arch-shaped composite curved surface in which a circumferential side surface of a pillar portion is formed by connecting an outer diameter side concave curved surface portion and an inner diameter side concave curved surface. Thus, regardless of the displacement of the rollers in the pocket, the rolling surfaces of the rollers and the radial end edges of the circumferential side surfaces of the column portions do not contact (per edge).

特開２００７−２７８４０６号公報JP 2007-278406 A

しかしながら、特許文献１に記載の保持器では、柱部の円周方向側面が２つの凹円弧同士を連続させてなるため、転動体が公転した際に、当該転動体と円周方向側面との接触が二面当たりとなってしまい、摩擦が大きくなってしまう問題が生じる。   However, in the cage described in Patent Document 1, since the circumferential side surface of the column portion is formed by connecting two concave arcs, when the rolling body revolves, the rolling body and the circumferential side surface There is a problem in that the contact comes into contact with two surfaces and the friction increases.

本発明は上記事情に鑑みてなされたものであり、転動体とポケット部との間で発生する摩擦を低減可能な転がり軸受用保持器を提供することを目的とする。   This invention is made | formed in view of the said situation, and it aims at providing the cage for rolling bearings which can reduce the friction which generate | occur | produces between a rolling element and a pocket part.

本発明の上記目的は、下記の構成により達成される。
（１） 周方向に所定間隔で配置された複数の柱部と、
隣り合う前記柱部の間に形成され、それぞれ転動体を転動自在に保持するポケット部と、
を備える転がり軸受用保持器であって、
前記ポケット部は、隣り合う前記柱部のうち、一方の前記柱部の第１円周方向側面と、他方の前記柱部の第２円周方向側面と、を有し、
前記第１及び第２円周方向側面は、それぞれ、第１及び第２中心軸を有する第１及び第２円筒面からなり、
前記第１及び第２中心軸は、円周方向位置が不同である、転がり軸受用保持器。
（２） 前記第１及び第２中心軸は、半径方向位置が同一である、（１）に記載の転がり軸受用保持器。
（３） 前記第１及び第２中心軸は、半径方向位置が不同である、（１）に記載の転がり軸受用保持器。
（４） 前記第１及び第２円筒面は、半径が同一である、（１）〜（３）の何れか１つに記載の転がり軸受用保持器。
（５） 前記第１及び第２円筒面は、半径が不同である、（１）〜（３）の何れか１つに記載の転がり軸受用保持器。
（６） 周方向に所定間隔で配置された複数の柱部と、
隣り合う前記柱部の間に形成され、それぞれ転動体を転動自在に保持するポケット部と、
を備える転がり軸受用保持器であって、
前記ポケット部は、隣り合う前記柱部のうち、一方の前記柱部の第１円周方向側面と、他方の前記柱部の第２円周方向側面と、を有し、
前記第１及び第２円周方向側面は、それぞれ、第１及び第２中心軸を有する第１及び第２円筒面と、前記第１及び第２円筒面と接続して平面形状である第１及び第２ストレート部と、からなり、
前記第１及び第２中心軸は、円周方向位置が不同である、転がり軸受用保持器。
（７） 前記転動体は、円筒ころである、（１）〜（６）の何れか１つに記載の転がり軸受用保持器。
（８） 前記転動体は、玉である、（１）〜（６）の何れか１つに記載の転がり軸受用保持器。 The above object of the present invention can be achieved by the following constitution.
(1) a plurality of pillars arranged at predetermined intervals in the circumferential direction;
A pocket portion formed between the adjacent column portions, each holding a rolling element so as to be freely rollable;
A rolling bearing retainer comprising:
The pocket portion includes a first circumferential side surface of one of the column portions and a second circumferential side surface of the other column portion among the adjacent column portions,
The first and second circumferential side surfaces comprise first and second cylindrical surfaces having first and second central axes, respectively.
The said 1st and 2nd center axis | shaft is a cage for rolling bearings where the circumferential direction position is not the same.
(2) The rolling bearing retainer according to (1), wherein the first and second central axes have the same radial position.
(3) The cage for a rolling bearing according to (1), wherein the first and second central axes have the same radial position.
(4) The rolling bearing retainer according to any one of (1) to (3), wherein the first and second cylindrical surfaces have the same radius.
(5) The rolling bearing retainer according to any one of (1) to (3), wherein the first and second cylindrical surfaces have radii that are the same.
(6) a plurality of pillars arranged at predetermined intervals in the circumferential direction;
A pocket portion formed between the adjacent column portions, each holding a rolling element so as to be freely rollable;
A rolling bearing retainer comprising:
The pocket portion includes a first circumferential side surface of one of the column portions and a second circumferential side surface of the other column portion among the adjacent column portions,
The first and second circumferential side surfaces are first and second cylindrical surfaces having first and second central axes, respectively, and are connected to the first and second cylindrical surfaces and have a planar shape. And the second straight part,
The said 1st and 2nd center axis | shaft is a cage for rolling bearings where the circumferential direction position is not the same.
(7) The rolling bearing retainer according to any one of (1) to (6), wherein the rolling element is a cylindrical roller.
(8) The rolling bearing retainer according to any one of (1) to (6), wherein the rolling element is a ball.

本発明の転がり軸受用保持器によれば、ポケット部を形成する第１及び第２円周方向側面は、それぞれ、第１及び第２中心軸を有する第１及び第２円筒面からなり、第１及び第２中心軸は、円周方向位置が不同である。したがって、転動体と保持器が半径方向に相対移動した場合には、保持器と転動体との接触が面当たりとなるので、転動体と柱部の円周方向側面の径方向端縁部とがエッジ当たりすることを回避できる。
また、第１及び第２円周方向側面がそれぞれ単一の円筒面である第１及び第２円筒面からなるので、転動体と保持器とが円周方向に相対移動した場合には、転動体と保持器とを一点で接触させることができる。
このように、接触面積が減少するので、転動体と保持器との間で発生する摺動摩擦を低減することが可能である。したがって、本発明の転がり軸受用保持器は、転動体と保持器との接触摩擦が大きい転動体案内形式の保持器に好適である。 According to the rolling bearing cage of the present invention, the first and second circumferential side surfaces forming the pocket portion are respectively composed of first and second cylindrical surfaces having first and second central axes, The circumferential positions of the first and second central axes are not the same. Therefore, when the rolling element and the cage move relative to each other in the radial direction, the contact between the cage and the rolling element comes into contact with the surface, so that the radial edge of the circumferential side surface of the rolling element and the column portion Can be prevented from hitting the edge.
In addition, since the first and second circumferential side surfaces are respectively composed of the first and second cylindrical surfaces which are single cylindrical surfaces, when the rolling element and the cage move relative to each other in the circumferential direction, the rolling The moving body and the cage can be brought into contact at a single point.
As described above, since the contact area is reduced, it is possible to reduce the sliding friction generated between the rolling elements and the cage. Therefore, the rolling bearing cage of the present invention is suitable for a rolling element guide type cage having a large contact friction between the rolling element and the cage.

本発明の第１実施形態に係る転がり軸受用保持器の斜視図である。1 is a perspective view of a rolling bearing retainer according to a first embodiment of the present invention. 図１の転がり軸受用保持器を軸方向から見た断面図である。It is sectional drawing which looked at the cage for rolling bearings of FIG. 1 from the axial direction. 保持器と転動体とが半径方向に相対移動した状態を示す断面図である。It is sectional drawing which shows the state which the cage | basket and the rolling element moved relative to the radial direction. 転動体が半径方向内側に移動した状態を示す断面図である。It is sectional drawing which shows the state which the rolling element moved to radial inside. 転動体が半径方向外側に移動した状態を示す断面図である。It is sectional drawing which shows the state which the rolling element moved to the radial direction outer side. （ａ）は第１実施形態の、（ｂ）〜（ｄ）は変形例の、第１及び第２中心並びに第１及び第２半径を示す図である。(A) is a figure which shows the 1st and 2nd center and 1st and 2nd radius of (b)-(d) of 1st Embodiment of a modification. 第２実施形態に係る転がり軸受用保持器を軸方向から見た断面図である。It is sectional drawing which looked at the cage for rolling bearings concerning 2nd Embodiment from the axial direction. 第３実施形態に係る転がり軸受用保持器を軸方向から見た断面図である。It is sectional drawing which looked at the cage for rolling bearings concerning 3rd Embodiment from the axial direction. 第１変形例に係る転がり軸受用保持器を半径方向から見た断面図である。It is sectional drawing which looked at the cage for rolling bearings which concerns on a 1st modification from the radial direction. 第２変形例に係る転がり軸受用保持器を半径方向から見た断面図である。It is sectional drawing which looked at the cage for rolling bearings which concerns on a 2nd modification from the radial direction. 第３変形例に係る転がり軸受用保持器を半径方向から見た断面図である。It is sectional drawing which looked at the rolling bearing retainer which concerns on a 3rd modification from the radial direction.

以下、本発明の実施形態に係る転がり軸受用保持器について、図面を用いて説明する。   Hereinafter, a rolling bearing retainer according to an embodiment of the present invention will be described with reference to the drawings.

（第１実施形態）
図１に示すように、本実施形態の転がり軸受用保持器１（以下、単に保持器と呼ぶ。）は、円周方向に所定間隔で配置された複数の柱部１０と、隣り合う柱部１０の間に形成され、それぞれ転動体３（図２参照）を転動自在に保持するポケット部２０と、複数の柱部１０の軸方向両端部と接続する一対の円環部３０と、を備える転動体案内形式のかご形状保持器である。 (First embodiment)
As shown in FIG. 1, the rolling bearing cage 1 (hereinafter simply referred to as a cage) of the present embodiment includes a plurality of column portions 10 arranged at predetermined intervals in the circumferential direction and adjacent column portions. 10, and each of the pocket portions 20 that holds the rolling elements 3 (see FIG. 2) so as to be freely rollable, and a pair of annular portions 30 that are connected to both axial ends of the plurality of column portions 10. It is a rolling body guide type cage-shaped cage provided.

図２も参照し、ポケット部２０は、隣り合う柱部１０のうち、一方の柱部１０の第１円周方向側面１１ａと、他方の柱部１０の第２円周方向側面１１ｂと、一対の円環部３０の軸方向側面３１と、から構成される。   Referring also to FIG. 2, the pocket part 20 includes a pair of adjacent pillar parts 10, a first circumferential side surface 11 a of one pillar part 10, a second circumferential side face 11 b of the other pillar part 10, and a pair. And an axial side surface 31 of the annular portion 30.

第１及び第２円周方向側面１１ａ、１１ｂは、それぞれ、第１及び第２中心軸Ｏａ、Ｏｂ並びに第１及び第２半径Ｒａ、Ｒｂを有する第１及び第２円筒面１２ａ、１２ｂからなる。すなわち、第１及び第２円周方向側面１１ａ、１１ｂはいわゆるゴシックアーチ形状に形成される。   The first and second circumferential side surfaces 11a, 11b are respectively composed of first and second cylindrical surfaces 12a, 12b having first and second central axes Oa, Ob and first and second radii Ra, Rb. . That is, the first and second circumferential side surfaces 11a and 11b are formed in a so-called gothic arch shape.

第１及び第２中心軸Ｏａ、Ｏｂは、互いに円周方向位置（図２における時計回り方向位置）が不同であり、半径方向位置（図２における上下方向位置）が同一である。第１及び第２半径Ｒａ、Ｒｂは、互いに等しく（Ｒａ＝Ｒｂ）、且つ転動体３の半径よりも大きく設定される。   The first and second central axes Oa and Ob have the same circumferential position (clockwise direction position in FIG. 2) and the same radial position (vertical direction position in FIG. 2). The first and second radii Ra and Rb are set equal to each other (Ra = Rb) and larger than the radius of the rolling element 3.

第１及び第２中心軸Ｏａ、Ｏｂの位置を適正値にずらし、第１及び第２半径Ｒａ、Ｒｂを適正値にすることにより、軸受回転中、図３に示すように保持器１と転動体３とが半径方向に相対移動した場合であっても、保持器１と転動体３との接触を面当たりとすることが可能となる。仮に、第１及び第２中心軸Ｏａ、Ｏｂが同一位置にあり、第１及び第２円周方向側面１１ａ、１１ｂが単一中心軸の円筒面であった場合、いかなる寸法関係においても、保持器１と転動体３との接触がエッジ当たりとなってしまう。すなわち、ポケット部２０の半径方向端縁部（エッジ部）と転動体３とが接触し、接触部の摩擦増大による不良や異常を引き起こす大きな要因となってしまう。本実施形態の保持器１は、この様なエッジ当たりを回避できるため、接触部の摩擦を低減することが可能である。   By shifting the positions of the first and second central axes Oa and Ob to appropriate values and setting the first and second radii Ra and Rb to appropriate values, the bearing 1 rotates with the cage 1 as shown in FIG. Even when the moving body 3 is relatively moved in the radial direction, the contact between the cage 1 and the rolling element 3 can be made per surface. If the first and second central axes Oa and Ob are in the same position, and the first and second circumferential side surfaces 11a and 11b are cylindrical surfaces of a single central axis, they are retained in any dimensional relationship. The contact between the vessel 1 and the rolling element 3 is per edge. That is, the edge part (edge part) of the pocket part 20 in the radial direction and the rolling element 3 come into contact with each other, which becomes a major factor causing defects and abnormalities due to increased friction at the contact part. Since the cage 1 of the present embodiment can avoid such edge contact, it is possible to reduce the friction of the contact portion.

上述の適正値とは、以下に示す条件を満たす数値である。図４には、保持器１が半径方向外側に移動し、当該保持器１の第１円周方向側面１１ａと転動体３とがｅで接触し、第２円周方向側面１１ｂと転動体３とがｆで接触している状態が示されている。また、第１円周方向側面１１ａの半径方向内側縁部がａで示され、半径方向外側縁部がｂで示され、第２円周方向側面１１ｂの半径方向内側縁部がｃで示され、半径方向外側縁部がｄで示されている。図４において、Ｙ軸方向は、第１及び第２円周方向側面１１ａ、１１ｂの周方向中間部を径方向に延びる中間線Ｍと同一方向であり、Ｘ軸方向は、Ｙ軸方向及び軸受回転軸方向と垂直の方向である。また、Ｙ軸は、軸受中心Ｏ及び保持器１の中心Ｏ１を通る軸であり、Ｘ軸は、保持器１の中心Ｏ１を通る軸である。このとき、Ｏａ、Ｏｂ、ａ〜ｆの座標はそれぞれ、（ＸＯａ、ＹＯａ）、（ＸＯｂ、ＹＯｂ）、（Ｘａ、Ｙａ）、（Ｘｂ、Ｙｂ）、（Ｘｃ、Ｙｃ）、（Ｘｄ、Ｙｄ）、（Ｘｅ、Ｙｅ）、（Ｘｆ、Ｙｆ）で、転動体３の直径はＷで、第１及び第２中心軸Ｏａ、Ｏｂの中間線Ｍ（Ｙ軸）からのＸ軸方向ずれ量はＬａ、Ｌｂで、転動体３のピッチ円直径はＰＣＤで示されている。 The appropriate value described above is a numerical value that satisfies the following conditions. In FIG. 4, the cage 1 moves radially outward, the first circumferential side surface 11 a of the cage 1 and the rolling element 3 come into contact with each other at e, and the second circumferential side surface 11 b and the rolling element 3 are in contact with each other. A state in which and are in contact with each other is shown. In addition, the radially inner edge of the first circumferential side surface 11a is denoted by a, the radially outer edge is denoted by b, and the radially inner edge of the second circumferential side surface 11b is denoted by c. The radially outer edge is indicated by d. In FIG. 4, the Y-axis direction is the same direction as the intermediate line M extending in the radial direction at the circumferential intermediate portions of the first and second circumferential side surfaces 11a, 11b, and the X-axis direction is the Y-axis direction and the bearing. This is a direction perpendicular to the rotation axis direction. Further, Y-axis is an axis passing through the center O 1 of the bearing center O and the cage 1, X-axis is an axis passing through the center O 1 of the cage 1. At this time, the coordinates of Oa, Ob, and a to f are (X Oa , Y Oa ), (X Ob , Y Ob ), (X a , Y a ), (X b , Y b ), and (X c ), respectively. , Y c ), (X d , Y d ), (X e , Y e ), (X f , Y f ), the diameter of the rolling element 3 is W, and the first and second central axes Oa, Ob The amounts of deviation in the X-axis direction from the intermediate line M (Y-axis) are La and Lb, and the pitch circle diameter of the rolling elements 3 is indicated by PCD.

このとき、接触点ｅは、（Ｌａ−Ｒａ）＜Ｘｅ＜Ｘａ、且つＹａ＜Ｙｅ＜Ｙｂを満たす。また、Ｘｅ及びＹｅは以下のように表される。

Figure 2016070423
Figure 2016070423
 At this time, the contact point e satisfies (La−Ra) <X e <X a and Y a <Y e <Y b . X e and Y e are expressed as follows.
Figure 2016070423
Figure 2016070423

また、同様に、接触点ｆは、Ｘｃ＜Ｘｆ＜（Ｒｂ−Ｌｂ）、且つＹｃ＜Ｙｆ＜Ｙｄを満たす。また、Ｘｆ及びＹｆは以下のように表される。

Figure 2016070423
Figure 2016070423
 Similarly, contact point f is, X c <X f <( Rb-Lb), and satisfies the Y c <Y f <Y d . X f and Y f are expressed as follows.
Figure 2016070423
Figure 2016070423

図５には、保持器１が半径方向内側に移動し、当該保持器１の第１円周方向側面１１ａと転動体３とがｇで接触し、第２円周方向側面１１ｂと転動体３とがｈで接触している状態が示されている。ここで、ｇ及びｈの座標はそれぞれ、（Ｘｇ、Ｙｇ）、（Ｘｈ、Ｙｈ）である。 In FIG. 5, the cage 1 moves inward in the radial direction, the first circumferential side surface 11 a of the cage 1 and the rolling element 3 come into contact with g, and the second circumferential side surface 11 b and the rolling element 3 are in contact with each other. A state in which and are in contact with each other is shown. Here, the coordinates of g and h are (X g , Y g ) and (X h , Y h ), respectively.

このとき、接触点ｇは、（Ｌａ−Ｒａ）＜Ｘｇ＜Ｘｂ、且つＹａ＜Ｙｇ＜Ｙｂを満たす。また、Ｘｇ及びＹｇは以下のように表される。

Figure 2016070423
Figure 2016070423
 At this time, the contact point g satisfies (La−Ra) <X g <X b and Y a <Y g <Y b . Xg and Yg are expressed as follows.
Figure 2016070423
Figure 2016070423

また、同様に、接触点ｈは、Ｘｄ＜Ｘｈ＜（Ｒｂ−Ｌｂ）、且つＹｃ＜Ｙｈ＜Ｙｄを満たす。また、Ｘｈ及びＹｈは以下のように表される。

Figure 2016070423
Figure 2016070423
 Similarly, the contact point h satisfies X d <X h <(Rb−Lb) and Y c <Y h <Y d . X h and Y h are expressed as follows.
Figure 2016070423
Figure 2016070423

このように、接触点ｅ〜ｈにおいて、保持器１の第１及び第２円周方向側面１１ａ、１１ｂと転動体３との接触条件が全て満たされるように設定される。   As described above, the contact points e to h are set so that all the contact conditions between the first and second circumferential side surfaces 11a and 11b of the cage 1 and the rolling element 3 are satisfied.

また、転動体３の公転によって、当該転動体３と保持器１とが円周方向に接触した場合であっても、第１及び第２円周方向側面１１ａ、１１ｂは、それぞれ転動体３の公転方向（円周方向）において単一の第１及び第２円筒面１２ａ、１２ｂからなるので、通常の保持器と同様に、転動体３と保持器１とを一点で接触させることができる。   Further, even when the rolling element 3 and the cage 1 are in contact with each other in the circumferential direction due to the revolution of the rolling element 3, the first and second circumferential side surfaces 11a and 11b are respectively in contact with the rolling element 3. Since it consists of single 1st and 2nd cylindrical surfaces 12a and 12b in a revolution direction (circumferential direction), the rolling element 3 and the holder | retainer 1 can be made to contact at one point similarly to a normal holder | retainer.

なお、軸受回転軸方向の自由度のためには、本実施形態のように、第１及び第２中心軸Ｏａ、Ｏｂの半径方向位置は同一であることが好ましく、第１及び第２円筒面１２ａ、１２ｂの第１及び第２半径Ｒａ、Ｒｂは同一であることが好ましい（図６（ａ）参照）。しかしながら、保持器暴れ抑制等の目的により、意図的に保持器１に拘束を与えるために、第１及び第２中心軸Ｏａ、Ｏｂの半径方向位置、並びに、第１及び第２半径Ｒａ、Ｒｂのうち、一方又は両方を異なる値としてもよい。例えば、図６（ｂ）に示すように、第１及び第２中心軸Ｏａ、Ｏｂの半径方向位置が不同であり、第１及び第２半径Ｒａ、Ｒｂが同一であってもよい。また、図６（ｃ）に示すように、第１及び第２中心軸Ｏａ、Ｏｂの半径方向位置が同一であり、第１及び第２半径Ｒａ、Ｒｂが不同であってもよい。また、図６（ｄ）に示すように、第１及び第２中心軸Ｏａ、Ｏｂの半径方向位置、並びに第１及び第２半径Ｒａ、Ｒｂが共に不同であってもよい。   For the degree of freedom in the bearing rotation axis direction, the radial positions of the first and second central axes Oa and Ob are preferably the same as in the present embodiment, and the first and second cylindrical surfaces The first and second radii Ra and Rb of 12a and 12b are preferably the same (see FIG. 6A). However, in order to intentionally constrain the cage 1 for the purpose of restraining the cage rampage, the radial positions of the first and second central axes Oa, Ob and the first and second radii Ra, Rb One or both of them may be different values. For example, as shown in FIG. 6B, the radial positions of the first and second central axes Oa and Ob may be the same, and the first and second radii Ra and Rb may be the same. Further, as shown in FIG. 6C, the radial positions of the first and second central axes Oa and Ob may be the same, and the first and second radii Ra and Rb may not be the same. Further, as shown in FIG. 6D, the radial positions of the first and second central axes Oa and Ob and the first and second radii Ra and Rb may not be the same.

また、保持器１の半径方向動き量は、第１及び第２中心軸Ｏａ、Ｏｂの座標、第１及び第２円筒面１２ａ、１２ｂの第１及び第２半径Ｒａ、Ｒｂ、転動体３の直径Ｗ、及び転動体３のピッチ円直径ＰＣＤの関係から決定される。これらの値は、軸受の用途により変更可能な数値であるが、いずれの値に設定したとしても、上述したエッジ当たりが回避可能な値となっていれば、同様の効果が発揮可能である。   The radial movement amount of the cage 1 includes the coordinates of the first and second central axes Oa and Ob, the first and second radii Ra and Rb of the first and second cylindrical surfaces 12a and 12b, and the rolling elements 3. It is determined from the relationship between the diameter W and the pitch circle diameter PCD of the rolling element 3. Although these values are numerical values that can be changed depending on the application of the bearing, even if any value is set, the same effect can be exhibited as long as the above-described edge contact can be avoided.

（第２実施形態）
次に、本発明の第２実施形態に係る転がり軸受用保持器１について、図７を用いて説明する。本実施形態の保持器１において、第１及び第２円周方向側面１１ａ、１１ｂは、第１及び第２中心軸Ｏａ、Ｏｂを有する第１及び第２円筒面１２ａ、１２ｂと、第１及び第２円筒面１２ａ、１２ｂの径方向外側端部と接続して平面形状である第１及び第２ストレート部１３ａ、１３ｂと、からなる。なお、第１及び第２円周方向側面１１ａ、１１ｂのうち、径方向内側の略半分が第１及び第２円筒面１２ａ、１２ｂとされ、径方向外側の略半分が第１及び第２ストレート部１３ａ、１３ｂとされる。また、本実施形態の第１及び第２ストレート部１３ａ、１３ｂは中間線Ｍと略平行となるように形成される。なお、第１及び第２ストレート部１３ａ、１３ｂは、径方向外側に向かうにしたがって、中間線Ｍから円周方向に離間するような形状としても構わない。 (Second Embodiment)
Next, a rolling bearing cage 1 according to a second embodiment of the present invention will be described with reference to FIG. In the cage 1 according to the present embodiment, the first and second circumferential side surfaces 11a and 11b include first and second cylindrical surfaces 12a and 12b having first and second central axes Oa and Ob, and first and second cylindrical surfaces 12a and 11b, respectively. The first and second straight portions 13a and 13b are connected to the radially outer ends of the second cylindrical surfaces 12a and 12b and have a planar shape. Of the first and second circumferential side surfaces 11a and 11b, approximately half of the radially inner side is defined as the first and second cylindrical surfaces 12a and 12b, and approximately half of the radially outer side is defined as the first and second straight surfaces. Parts 13a and 13b. Further, the first and second straight portions 13 a and 13 b of the present embodiment are formed so as to be substantially parallel to the intermediate line M. Note that the first and second straight portions 13a and 13b may be shaped so as to be separated from the intermediate line M in the circumferential direction toward the radially outer side.

このように構成することで、保持器１の半径方向の動き量の規制が、第１及び第２円筒面１２ａ、１２ｂによるもののみとなるため、転動体３と保持器１の接触位置のランダム性が減少し、保持器１の動きを安定させることが可能となる。また、運転時の遠心力により保持器１が膨張する際、転動体３公転方向（円周方向）のポケット部２０の隙間増大に合わせて、保持器１の径も大きくなるため、相対的に保持器１の半径方向動き量の増大を抑制し、又は減少させることが可能となる。   With this configuration, since the restriction of the amount of movement of the cage 1 in the radial direction is limited only by the first and second cylindrical surfaces 12a and 12b, the contact position between the rolling element 3 and the cage 1 is random. Therefore, the movement of the cage 1 can be stabilized. In addition, when the cage 1 expands due to the centrifugal force during operation, the diameter of the cage 1 increases as the gap of the pocket portion 20 in the rolling direction of the rolling element 3 (circumferential direction) increases. It is possible to suppress or reduce an increase in the amount of radial movement of the cage 1.

（第３実施形態）
次に、本発明の第３実施形態に係る転がり軸受用保持器１について、図８を用いて説明する。本実施形態の保持器１において、第１及び第２円周方向側面１１ａ、１１ｂは、第１及び第２中心軸Ｏａ、Ｏｂを有する第１及び第２円筒面１２ａ、１２ｂと、第１及び第２円筒面１２ａ、１２ｂの径方向内側端部と接続して平面形状である第１及び第２ストレート部１３ａ、１３ｂと、からなる。なお、第１及び第２円周方向側面１１ａ、１１ｂのうち、径方向外側の略半分が第１及び第２円筒面１２ａ、１２ｂとされ、径方向内側の略半分が第１及び第２ストレート部１３ａ、１３ｂとされる。また、本実施形態の第１及び第２ストレート部１３ａ、１３ｂは中間線Ｍと略平行となるように形成される。なお、第１及び第２ストレート部１３ａ、１３ｂは、径方向内側に向かうにしたがって、中間線Ｍから円周方向に離間するような形状としても構わない。 (Third embodiment)
Next, a rolling bearing cage 1 according to a third embodiment of the present invention will be described with reference to FIG. In the cage 1 according to the present embodiment, the first and second circumferential side surfaces 11a and 11b include first and second cylindrical surfaces 12a and 12b having first and second central axes Oa and Ob, and first and second cylindrical surfaces 12a and 11b, respectively. The first and second straight portions 13a and 13b are connected to the radially inner ends of the second cylindrical surfaces 12a and 12b and have a planar shape. Of the first and second circumferential side surfaces 11a and 11b, approximately half of the radially outer side is defined as the first and second cylindrical surfaces 12a and 12b, and approximately half of the radially inner side is defined as the first and second straight surfaces. Parts 13a and 13b. Further, the first and second straight portions 13 a and 13 b of the present embodiment are formed so as to be substantially parallel to the intermediate line M. The first and second straight portions 13a and 13b may be shaped so as to be separated from the intermediate line M in the circumferential direction toward the radially inner side.

このように構成することで、保持器１の半径方向の動き量の規制が、第１及び第２円筒面１２ａ、１２ｂによるもののみとなるため、転動体３と保持器１の接触位置のランダム性が減少し、保持器１の動きを安定させることが可能となる。また、本実施形態では、遠心力の増大により、保持器１の動き量を大きくできるので、保持器１の膨張による第１及び第２円筒面１２ａ、１２ｂと転動体３との干渉の発生を回避できるとともに、保持器１の半径方向動き量の初期値を極限まで小さく設定することが可能となる。   With this configuration, since the restriction of the amount of movement of the cage 1 in the radial direction is limited only by the first and second cylindrical surfaces 12a and 12b, the contact position between the rolling element 3 and the cage 1 is random. Therefore, the movement of the cage 1 can be stabilized. In the present embodiment, since the amount of movement of the cage 1 can be increased by increasing the centrifugal force, the interference between the first and second cylindrical surfaces 12a and 12b and the rolling element 3 due to the expansion of the cage 1 is prevented. This can be avoided, and the initial value of the radial movement amount of the cage 1 can be set as small as possible.

尚、本発明は、前述した実施形態に限定されるものではなく、適宜変更、改良等が可能である。   In addition, this invention is not limited to embodiment mentioned above, A change, improvement, etc. are possible suitably.

（第１変形例）
例えば、本発明の保持器１は、図９に示すように、円筒ころ軸受のかご形状保持器に適用することが可能である。第１及び第２円周方向側面１１ａ、１１ｂの形状は、第１〜第３実施形態のうち、何れの構成を適用しても構わない。当該構成によれば、上述したように、転動体３としての円筒ころと、ポケット部２０の半径方向端縁部（エッジ部）との接触を防止できるので、転動体３と保持器１との間の摩擦を低減することが可能である。 (First modification)
For example, the cage 1 of the present invention can be applied to a cage-shaped cage of a cylindrical roller bearing as shown in FIG. Any of the configurations of the first and third embodiments may be applied to the shapes of the first and second circumferential side surfaces 11a and 11b. According to the configuration, as described above, contact between the cylindrical roller as the rolling element 3 and the radial end edge (edge part) of the pocket portion 20 can be prevented. It is possible to reduce the friction between them.

（第２変形例）
また、本発明の保持器１は、図１０に示すように、玉軸受のかご形状保持器１に適用することが可能である。第１及び第２円周方向側面１１ａ、１１ｂの形状は、第１〜第３実施形態のうち、何れの構成を適用しても構わない。当該構成によれば、転動体３としての玉とポケット部２０との接触箇所が、ポケット部２０を構成する各壁面（第１及び第２円周方向側面１１ａ、１１ｂ、並びに一対の円環部３０の軸方向側面３１。）に対して一点ずつとなるため、摺動面積を非常に小さくすることができ、摺動摩擦を大きく低減することが可能である。 (Second modification)
Further, the cage 1 of the present invention can be applied to a cage-shaped cage 1 of a ball bearing as shown in FIG. Any of the configurations of the first and third embodiments may be applied to the shapes of the first and second circumferential side surfaces 11a and 11b. According to the said structure, the contact location of the ball | bowl as the rolling element 3, and the pocket part 20 is each wall surface (1st and 2nd circumferential side surface 11a, 11b, and a pair of annular part which comprises the pocket part 20). 30), the sliding area can be made very small and the sliding friction can be greatly reduced.

（第３変形例）
また、本発明の保持器１は、図１１に示すように、複列円筒ころ軸受のくし形状保持器に適用することが可能である。この保持器１は、円環部３０の軸方向両側面３１から軸方向両側に延在する複数の柱部１０を備える。ポケット部２０は、隣り合う柱部１０のうち、一方の柱部１０の第１円周方向側面１１ａと、他方の柱部１０の第２円周方向側面１１ｂと、円環部３０の軸方向側面３１と、から構成される。第１及び第２円周方向側面１１ａ、１１ｂの形状は、第１〜第３実施形態のうち、何れの構成を適用しても構わない。当該構成によれば、上述の第１変形例（図９参照）と比較して、１つの転動体３に対するポケット部２０の壁面数を少なくできるので、摺動面積を小さくでき、摺動摩擦を低減することが可能である。 (Third Modification)
Moreover, the cage 1 of the present invention can be applied to a comb-shaped cage of a double row cylindrical roller bearing as shown in FIG. The cage 1 includes a plurality of column portions 10 extending from both axial side surfaces 31 of the annular portion 30 to both axial sides. The pocket portion 20 includes the first circumferential side surface 11 a of one column portion 10, the second circumferential side surface 11 b of the other column portion 10, and the axial direction of the annular portion 30 among the adjacent column portions 10. And a side surface 31. Any of the configurations of the first and third embodiments may be applied to the shapes of the first and second circumferential side surfaces 11a and 11b. According to the said structure, compared with the above-mentioned 1st modification (refer FIG. 9), since the number of wall surfaces of the pocket part 20 with respect to one rolling element 3 can be decreased, a sliding area can be made small and a sliding friction is reduced. Is possible.

１ 転がり軸受用保持器
３ 転動体
１０ 柱部
１１ａ 第１円周方向側面
１２ａ 第１円筒面
１３ａ 第１ストレート部
１１ｂ 第２円周方向側面
１２ｂ 第２円筒面
１３ｂ 第２ストレート部
２０ ポケット部
３０ 円環部
３１ 軸方向側面
Ｌａ Ｘ軸方向ずれ量
Ｍ 中間線
Ｏａ 第１中心軸
Ｏｂ 第２中心軸
ＰＣＤ ピッチ円直径
Ｒａ 第１半径
Ｒｂ 第２半径
Ｗ 転動体の直径 DESCRIPTION OF SYMBOLS 1 Rolling bearing cage 3 Rolling body 10 Column 11a First circumferential side surface 12a First cylindrical surface 13a First straight portion 11b Second circumferential side surface 12b Second cylindrical surface 13b Second straight portion 20 Pocket portion 30 Annular portion 31 Axial side surface La X-axis direction deviation amount M Middle line Oa First central axis Ob Second central axis PCD Pitch circle diameter Ra First radius Rb Second radius W Diameter of rolling element

Claims (8)

周方向に所定間隔で配置された複数の柱部と、
隣り合う前記柱部の間に形成され、それぞれ転動体を転動自在に保持するポケット部と、
を備える転がり軸受用保持器であって、
前記ポケット部は、隣り合う前記柱部のうち、一方の前記柱部の第１円周方向側面と、他方の前記柱部の第２円周方向側面と、を有し、
前記第１及び第２円周方向側面は、それぞれ、第１及び第２中心軸を有する第１及び第２円筒面からなり、
前記第１及び第２中心軸は、円周方向位置が不同である、転がり軸受用保持器。 A plurality of pillars arranged at predetermined intervals in the circumferential direction;
A pocket portion formed between the adjacent column portions, each holding a rolling element so as to be freely rollable;
A rolling bearing retainer comprising:
The pocket portion includes a first circumferential side surface of one of the column portions and a second circumferential side surface of the other column portion among the adjacent column portions,
The first and second circumferential side surfaces comprise first and second cylindrical surfaces having first and second central axes, respectively.
The said 1st and 2nd center axis | shaft is a cage for rolling bearings where the circumferential direction position is not the same. 前記第１及び第２中心軸は、半径方向位置が同一である、請求項１に記載の転がり軸受用保持器。   The rolling bearing retainer according to claim 1, wherein the first and second central axes have the same radial position. 前記第１及び第２中心軸は、半径方向位置が不同である、請求項１に記載の転がり軸受用保持器。   The rolling bearing retainer according to claim 1, wherein the first and second central axes have the same radial position. 前記第１及び第２円筒面は、半径が同一である、請求項１〜３の何れか１項に記載の転がり軸受用保持器。   The rolling bearing retainer according to any one of claims 1 to 3, wherein the first and second cylindrical surfaces have the same radius. 前記第１及び第２円筒面は、半径が不同である、請求項１〜３の何れか１項に記載の転がり軸受用保持器。   The rolling bearing retainer according to any one of claims 1 to 3, wherein the first and second cylindrical surfaces have the same radius. 周方向に所定間隔で配置された複数の柱部と、
隣り合う前記柱部の間に形成され、それぞれ転動体を転動自在に保持するポケット部と、
を備える転がり軸受用保持器であって、
前記ポケット部は、隣り合う前記柱部のうち、一方の前記柱部の第１円周方向側面と、他方の前記柱部の第２円周方向側面と、を有し、
前記第１及び第２円周方向側面は、それぞれ、第１及び第２中心軸を有する第１及び第２円筒面と、前記第１及び第２円筒面と接続して平面形状である第１及び第２ストレート部と、からなり、
前記第１及び第２中心軸は、円周方向位置が不同である、転がり軸受用保持器。 A plurality of pillars arranged at predetermined intervals in the circumferential direction;
A pocket portion formed between the adjacent column portions, each holding a rolling element so as to be freely rollable;
A rolling bearing retainer comprising:
The pocket portion includes a first circumferential side surface of one of the column portions and a second circumferential side surface of the other column portion among the adjacent column portions,
The first and second circumferential side surfaces are first and second cylindrical surfaces having first and second central axes, respectively, and are connected to the first and second cylindrical surfaces and have a planar shape. And the second straight part,
The said 1st and 2nd center axis | shaft is a cage for rolling bearings where the circumferential direction position is not the same. 前記転動体は、円筒ころである、請求項１〜６の何れか１項に記載の転がり軸受用保持器。   The rolling bearing retainer according to claim 1, wherein the rolling element is a cylindrical roller. 前記転動体は、玉である、請求項１〜６の何れか１項に記載の転がり軸受用保持器。
The rolling bearing retainer according to any one of claims 1 to 6, wherein the rolling element is a ball.
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