JP2010286119A - Ball bearing - Google Patents

Ball bearing Download PDF

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JP2010286119A
JP2010286119A JP2010159006A JP2010159006A JP2010286119A JP 2010286119 A JP2010286119 A JP 2010286119A JP 2010159006 A JP2010159006 A JP 2010159006A JP 2010159006 A JP2010159006 A JP 2010159006A JP 2010286119 A JP2010286119 A JP 2010286119A
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Prior art keywords
balls
claw pieces
ball
ball bearing
cage
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JP5029733B2 (en
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Susumu Tanaka
進 田中
Yoshiteru Sakajiri
義晃 坂尻
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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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a ball bearing which decreases an agitation resistance of a lubricating oil to realize a low torque, even when the ball diameter or the number of balls is decreased. <P>SOLUTION: There are provided an inner ring, an outer ring, a ball bearing equipped with a plurality of balls 14 arranged in a freely rollable manner between the inner and outer rings, and a plastic retainer 2 provided with a plurality of pockets 12 for holding the balls 14 at given intervals along the circumferential direction of the retainer 2. In the ball bearing, the distance between balls held in adjacent pockets 12 is equal to or more than twice the ball diameter. The retainer forms a pair of claw pieces 16a, 16b making up the opening end of each pocket, a separating portion, and a protrusion 13 which rises axially from the separating portion and is formed with a surface flat in the axial end and besides is formed in a circular-arch shape when axially viewed and is further provided between adjacent pockets. Heights from the bottoms of the separating portions between the protrusions 13 and the claw pieces 16a, 16b are the same. Furthermore, the radial widths of the protrusion 13 and claw pieces 16a, 16b are the same. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、自動車のトランスミッションなどに好ましく用いられる玉軸受に関し、更に詳しくは、プラスチック製の冠型保持器を備えた玉軸受に関する。   The present invention relates to a ball bearing preferably used for a transmission of an automobile, and more particularly to a ball bearing provided with a plastic crown-shaped cage.

一般に、自動車のトランスミッションなどのように、油潤滑下で用いられる深溝玉軸受は、転動体である玉、内輪、外輪の材料として、軸受鋼であればＳＵＪ２が、肌焼鋼であればＳＣＲ４２０やＳＣＭ４２０相当の鋼材等が用いられる。また、玉を転動自在に保持するための保持器には、ＳＰＣＣからなる鉄製の波形プレス保持器又はプラスチック製の冠型保持器が使用される。   In general, deep groove ball bearings used under oil lubrication, such as automobile transmissions, are SUJ2 for bearing steel and SCR420 for case-hardened steel as materials for balls, inner rings and outer rings as rolling elements. A steel material or the like equivalent to SCM420 is used. In addition, an iron corrugated press holder made of SPCC or a plastic crown holder is used as a holder for holding the balls so as to roll freely.

近年、環境問題の高まりから、自動車のトランスミッションを構成する軸受部品においても、極めて低トルク化のニーズが高まっている。   In recent years, due to increasing environmental problems, there is an increasing need for extremely low torque in bearing parts constituting automobile transmissions.

玉軸受の摩擦損失トルクの原因として、［１］内外輪と玉との間の転がり摩擦、［２］
内外輪と玉との間のすべり摩擦、［３］玉と保持器とのすべり摩擦、［４］潤滑油の撹拌抵抗等があるが、玉軸受の低トルク化を達成する手段としては、負荷条件の軽減、軸受のサイズダウンが一般的である。 Causes of friction loss torque of ball bearings are [1] rolling friction between inner and outer rings and balls, [2]
Sliding friction between inner and outer rings and balls, [3] Sliding friction between balls and cage, [4] Stirring resistance of lubricating oil, etc. Reduction of conditions and downsizing of bearings are common.

しかしながら、このような手段においては、軸受寿命や剛性低下あるいは軸受取付周辺構造が制約される等の問題がある。   However, in such a means, there are problems such as a decrease in bearing life and rigidity, or a restriction on a bearing mounting peripheral structure.

また、上記［３］の観点では、近年では、トランスミッション用の玉軸受に、軽量かつ自己潤滑性に優れるプラスチック製の保持器が使用されることも増えている。   In addition, from the viewpoint of the above [3], in recent years, plastic cages that are lightweight and have excellent self-lubricating properties are increasingly used for transmission ball bearings.

また、上記［４］の観点では、軸受への供給油量の低減又は潤滑油の低粘度化などが考えられるが、これらの手段では、軸受、ユニットの性能面で制約を受けたり、当該ユニットの動作条件（例えば、エンジンあるいはその他の回転部材の回転数）にも影響を受けるため、上記手法においてはコントロールし難いという問題がある。   Further, from the viewpoint of the above [4], it is conceivable to reduce the amount of oil supplied to the bearing or to lower the viscosity of the lubricating oil. However, with these means, there are restrictions on the performance of the bearing and unit, This method is also affected by the operating conditions (for example, the number of revolutions of the engine or other rotating members), so that there is a problem that it is difficult to control in the above method.

一般に、トランスミッションにおいて使用される玉軸受は、特に、軸受寿命に対する要求が厳しく、特別な場合を除いては、内輪と外輪との間の空間にできるだけ玉を入れて、与えられたスペースの中で、定格荷重を最大限大きくするような設計がなされるのが一般的である。しかし、以上のような観点から、与えられた寸法の中で、最大限にトルク低減を可能にするためには、玉径及び玉数の最適化などの手法が有効となる。   In general, ball bearings used in transmissions have particularly strict bearing life requirements. Unless otherwise specified, balls are placed in the space between the inner ring and the outer ring as much as possible within the given space. In general, a design that maximizes the rated load is made. However, in view of the above, techniques such as optimization of the ball diameter and the number of balls are effective in order to enable torque reduction to the maximum within a given dimension.

従来の玉軸受用の保持器として、図８及び図９に示す冠型の構成のものがある（例えば、特許文献１参照）。図８は保持器の斜視図であり、図９は図８の保持器の部分展開図である。   As a conventional cage for ball bearings, there is a crown type structure shown in FIGS. 8 and 9 (see, for example, Patent Document 1). 8 is a perspective view of the cage, and FIG. 9 is a partial development view of the cage of FIG.

保持器３１はプラスチック製であり、いわゆる冠型に成形され、環状の保持器本体３２は、軸方向の一方の面に、軸方向に向いて開口して玉を転動自在にかつ脱落不能に保持する複数のポケット３５を円周方向に並んで有する。ポケット３５は等間隔とされている。   The cage 31 is made of plastic and is formed into a so-called crown shape, and the annular cage body 32 opens on one axial surface in the axial direction so that the balls can roll and cannot be dropped. A plurality of pockets 35 to be held are arranged in the circumferential direction. The pockets 35 are equally spaced.

これらポケット３５の開口端部は、ポケット開口の保持器本体周方向の両側に位置する一対の爪片３３ａ，３３ｂにより形成され、ポケット３５の内面は球面状とされている。ポケット３５の両側の爪片３３ａ，３３ｂは、互いに先端が近づく形状とされ、爪片３３ａ，３３ｂ間の入口径は玉径よりも小さくされている。   The opening end portions of these pockets 35 are formed by a pair of claw pieces 33a and 33b located on both sides of the pocket opening in the circumferential direction of the cage body, and the inner surface of the pocket 35 is spherical. The claw pieces 33a and 33b on both sides of the pocket 35 are shaped so that the tips approach each other, and the entrance diameter between the claw pieces 33a and 33b is smaller than the ball diameter.

軸受の組み付けは、この爪片３３ａ，３３ｂの先端を玉３６でわずかに押し広げるスナップオン方式によって行われる。つまり、上記保持器３１に形成された爪片３３ａ，３３ｂはある程度自由に変形することが必要であり、剛性が高すぎると、組み付け性が低下したり、組み付け時に保持器３１が破損したり、永久変形により玉挿入口である開口部が大きくなって回転中に保持器３１が外れ易くなる恐れがある。   The assembly of the bearing is performed by a snap-on method in which the tips of the claw pieces 33a and 33b are slightly pushed by the balls 36. In other words, the claw pieces 33a and 33b formed on the cage 31 need to be freely deformed to some extent. If the rigidity is too high, the assembling property is lowered, or the cage 31 is damaged during the assembly, Due to the permanent deformation, the opening that is the ball insertion opening becomes large, and the cage 31 may be easily detached during rotation.

したがって、一般的なプラスチック製の保持器３１は、隣接する各ポケット３５間における爪片３３ａ，３３ｂの間に凹部３４があり、上記爪片３３ａ，３３ｂの弾性変形を可能にしている。   Therefore, the general plastic retainer 31 has a recess 34 between the claw pieces 33a and 33b between the adjacent pockets 35, so that the claw pieces 33a and 33b can be elastically deformed.

また、図９に示すように、一般にポケット３４内の玉３６間の距離Ｌは、
Ｌ＝πｄｍ／ｚ （ｄｍ：ＰＣＤ、ｚ：玉数）
となるように設定されている。 Further, as shown in FIG. 9, generally, the distance L between balls 36 in the pocket 34 is:
L = π dm / z (dm: PCD, z: number of balls)
It is set to become.

特開２００３−３２９０４５号公報（図２）Japanese Patent Laying-Open No. 2003-329045 (FIG. 2)

しかしながら、これらの爪片３３ａ，３３ｂは、保持器本体３２から湾曲しながら異なる方向に突出するという複雑な形状をしているため、軸受の回転時に不要に潤滑油を撹拌するという問題がある。   However, these claw pieces 33a and 33b have a complicated shape of projecting in different directions while curving from the cage main body 32, so that there is a problem that the lubricating oil is unnecessarily agitated when the bearing rotates.

したがって、トルク低減のために、玉径を小さくしたり、玉数を減らすと、保持器３１の正面側（ポケット側）に設けられた爪片３３ａ，３３ｂによる潤滑油の撹拌抵抗による影響が無視できない。特に軸受のＰＣＤ（ピッチ円直径）が大きい場合は、爪片３３ａ，３３ｂによる潤滑油の撹拌抵抗の影響が大きい。   Therefore, if the ball diameter is reduced or the number of balls is reduced in order to reduce torque, the influence of the stirring resistance of the lubricating oil by the claw pieces 33a and 33b provided on the front side (pocket side) of the cage 31 is ignored. Can not. In particular, when the bearing has a large PCD (pitch circle diameter), the influence of the lubricating oil stirring resistance by the claw pieces 33a and 33b is large.

本発明の目的は、上記問題を解決することにあり、玉径を小さくしたり玉数を減らしたりした場合でも、潤滑油の撹拌抵抗を小さくでき低トルク化が可能な玉軸受を提供することにある。   An object of the present invention is to solve the above problem, and to provide a ball bearing capable of reducing the stirring resistance of the lubricating oil and reducing the torque even when the ball diameter is reduced or the number of balls is reduced. It is in.

本発明の上記目的は、下記構成により達成される。   The above object of the present invention is achieved by the following configurations.

（１）内輪と、
外輪と、
前記内輪と前記外輪との間に転動自在に配設された複数の玉と、
前記玉を円周方向に沿って所定間隔に保持する複数のポケットが設けられたプラスチック製保持器と、を備えた玉軸受において、
隣接する前記ポケットに保持された玉間距離Ｌが、玉径Ｄａの２倍以上であることを特徴とする玉軸受。 (1) inner ring,
Outer ring,
A plurality of balls arranged to roll between the inner ring and the outer ring;
In a ball bearing comprising a plastic cage provided with a plurality of pockets for holding the balls at a predetermined interval along the circumferential direction,
A ball bearing characterized in that the distance L between the balls held in the adjacent pockets is at least twice the ball diameter Da.

（２）前記保持器は、
環状の保持器本体と、
前記各ポケットの開口端を構成する一対の爪片と、
前記一対の爪片の円周方向外側に設けられた離間部と、
前記離間部から軸方向に立ち上がり軸方向端部が平坦面を形成し、且つ、軸方向から見て円弧状に形成され、隣接する前記ポケット間に設けられた凸部と、を備え、
前記凸部と前記爪片との前記離間部の底面からの高さは同じ高さに設定されており、
前記凸部と前記爪片との半径方向の幅は同じ幅に設定されていることを特徴とする自動車用トランスミッションに使用される（１）に記載の玉軸受。 (2) The cage is
An annular cage body;
A pair of claw pieces constituting the open end of each pocket;
A spacing portion provided on the outer circumferential side of the pair of claw pieces;
The rising end in the axial direction from the spaced apart part forms a flat surface, and is formed in an arc shape when viewed from the axial direction, and includes a convex part provided between the adjacent pockets,
The height from the bottom surface of the spacing portion between the convex portion and the claw piece is set to the same height,
The ball bearing according to (1), which is used in an automobile transmission, characterized in that a radial width of the convex portion and the claw piece is set to the same width.

本発明の玉軸受によれば、玉数を減らしたりした場合に、保持器の爪片による潤滑油の撹拌抵抗を大幅に低減することができるので、軸受の低トルク化が可能になる。   According to the ball bearing of the present invention, when the number of balls is reduced, the agitation resistance of the lubricating oil by the claw pieces of the cage can be greatly reduced, so that the torque of the bearing can be reduced.

本発明の構成は、特に、軸受のＰＣＤが大きくかつ玉数が少ない場合に有効である。
また、本発明の玉軸受は、例えば自動車用トランスミッションにおいて、低フリクションと高速回転化に有効であり、ハイブリッド車に好適に用いられる。 The configuration of the present invention is particularly effective when the bearing PCD is large and the number of balls is small.
The ball bearing of the present invention is effective for low friction and high speed rotation in, for example, an automobile transmission, and is preferably used for a hybrid vehicle.

本発明の第１実施形態である保持器の斜視図である。It is a perspective view of the holder | retainer which is 1st Embodiment of this invention. 本発明の第１実施形態である玉軸受の要部断面図である。It is principal part sectional drawing of the ball bearing which is 1st Embodiment of this invention. 本発明の第１実施形態の保持器の部分展開図である。It is a partial expanded view of the holder | retainer of 1st Embodiment of this invention. 図３の要部拡大図である。It is a principal part enlarged view of FIG. 本発明の第２実施形態である保持器の斜視図である。It is a perspective view of the holder | retainer which is 2nd Embodiment of this invention. 本発明の第２実施形態の保持器の部分展開図である。It is a partial expanded view of the holder | retainer of 2nd Embodiment of this invention. 図６の要部拡大図である。It is a principal part enlarged view of FIG. 従来の保持器の斜視図である。It is a perspective view of the conventional holder | retainer. 図９の保持器の部分展開図である。FIG. 10 is a partial development view of the cage of FIG. 9.

以下、添付図面を参照して本発明の実施形態を説明する。
図１は、本発明の第１実施形態である玉軸受用プラスチック製保持器の斜視図、図２は本発明の第１実施形態である玉軸受の要部断面図、図３は本発明の第１実施形態の保持器の部分展開図、図４は図３の要部拡大図である。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
FIG. 1 is a perspective view of a plastic cage for ball bearings according to a first embodiment of the present invention, FIG. 2 is a cross-sectional view of an essential part of the ball bearing according to the first embodiment of the present invention, and FIG. FIG. 4 is a partial development view of the cage of the first embodiment, and FIG. 4 is an enlarged view of a main part of FIG.

図２に示すように、玉軸受１は、玉１４を保持したプラスチック製の保持器２を内輪３及び外輪４の間に組み込んだものである。   As shown in FIG. 2, the ball bearing 1 is obtained by incorporating a plastic cage 2 holding a ball 14 between an inner ring 3 and an outer ring 4.

保持器２は、図１に示す環状の保持器本体１１に所定間隔でポケット１２と、後述する凸部１３とを一体成形し、各ポケット１２に玉１４をスナップオン方式で嵌め込む構成になっている。ポケット１２は、保持器本体１１に所定量の等間隔で設けられる。なお、ポケット１２の数は、必要に応じて自在に変更できる。   The cage 2 has a configuration in which a pocket 12 and a convex portion 13 described later are integrally formed at a predetermined interval in an annular cage body 11 shown in FIG. 1 and a ball 14 is fitted into each pocket 12 by a snap-on method. ing. The pockets 12 are provided in the retainer body 11 at a predetermined amount of regular intervals. The number of pockets 12 can be freely changed as necessary.

本実施形態では、合計５個のポケット１２が図示されているが、各ポケット１２の構成は同一であるので、それぞれ共通の符号を付して説明する。ポケット１２の開口端は、弾性を有する一対の爪片１６ａ，１６ｂにより形成され、爪片１６ａ，１６ｂの対向する側面は玉１４を転動自在に保持するように曲面になっている。   In the present embodiment, a total of five pockets 12 are illustrated, but since the configuration of each pocket 12 is the same, a description will be given with a common reference. The opening end of the pocket 12 is formed by a pair of elastic claw pieces 16a and 16b, and the opposing side surfaces of the claw pieces 16a and 16b are curved so as to hold the ball 14 in a freely rollable manner.

一対の爪片１６ａ，１６ｂの上端部は、図４に拡大して示すように、玉の直径Ｄａに対し小幅Ｗに設定されている。したがって、図４に想像線で示すように、ポケット１２の開口部から玉を押し込むと、一対の爪片１６ａ，１６ｂが想像線で示すようにわずかに開く。そして、玉１４を更に押し込むことにより、玉１４は一対の爪片１６ａ，１６ｂの弾性力に抗してポケット１２内に入り込み、転動自在に収納されて保持される。   The upper ends of the pair of claw pieces 16a and 16b are set to have a small width W with respect to the diameter Da of the ball as shown in an enlarged manner in FIG. Therefore, as shown by an imaginary line in FIG. 4, when a ball is pushed in from the opening of the pocket 12, the pair of claw pieces 16a and 16b are slightly opened as indicated by the imaginary line. Further, by pushing the ball 14 further, the ball 14 enters the pocket 12 against the elastic force of the pair of claw pieces 16a and 16b, and is stored and held so as to be able to roll.

すなわち、スナップオン方式で玉１４がポケット１２内に収納され、転動自在に保持されるのであるが、収納状態では一対の爪片１６ａ，１６ｂが図４に実線で示すように、元の形状に復帰し玉１４を保持するようになる。したがって、玉１４がポケットから抜け出すことはなく、安定に転動することができる。   In other words, the ball 14 is stored in the pocket 12 by the snap-on method and is held so as to be able to roll. However, in the stored state, the pair of claw pieces 16a and 16b have an original shape as shown by a solid line in FIG. The ball 14 is held again. Therefore, the ball 14 does not come out of the pocket and can roll stably.

一対の爪片１６ａ，１６ｂの周方向に沿った外側には、離間部１８ａ，１８ｂを介して凸部１３が形成されている。そして、凸部１３の周方向の両端の側面は、１〜５°程度のテーパ面に形成されるとともに、凸部１３の頂部は平坦に形成されている。   On the outer side along the circumferential direction of the pair of claw pieces 16a and 16b, a convex portion 13 is formed via spacing portions 18a and 18b. And the side surface of the both ends of the circumferential direction of the convex part 13 is formed in the taper surface of about 1-5 degrees, and the top part of the convex part 13 is formed flat.

離間部１８ａ，１８ｂの底面からの凸部１３の高さＨは爪片１６ａ，１６ｂの高さと同じであり、高さＨは玉の半径（Ｄａ／２）以下に設定されている。すなわち、玉の直径をＤａとした場合、Ｈ≦Ｄａ／２の関係に設定されている。この高さＨは離間部１８ａ，１８ｂの深さを変えることにより自在に設定される。また、離間部１８ａ，１８ｂの底面の隅部及び凸部１３の角部は０．２Ｒ程度に丸みが設定されている。   The height H of the convex portion 13 from the bottom surface of the spacing portions 18a and 18b is the same as the height of the claw pieces 16a and 16b, and the height H is set to be equal to or less than the radius (Da / 2) of the ball. That is, when the diameter of the ball is Da, a relationship of H ≦ Da / 2 is set. This height H is freely set by changing the depth of the separating portions 18a and 18b. Further, the corners of the bottom surfaces of the separating portions 18a and 18b and the corner portions of the convex portion 13 are set to be rounded to about 0.2R.

凸部１３は、保持器本体１１に設けられた各ポケット１２間に、軸方向から見た状態で円弧状に形成されている。各ポケット１２の中心間の間隔をＬとし、玉１４の径をＤａとすると、図３に示すように、Ｌ＝２Ｄａ〜５Ｄａ程度に設定されている。そして、凸部１３は各ポケット１２から離間部１８ａ，１８ｂを介してテーパ状に立ち上がり、軸方向端部が平坦に形成されている。   The convex portion 13 is formed in an arc shape between the pockets 12 provided in the cage body 11 as viewed from the axial direction. When the interval between the centers of the pockets 12 is L and the diameter of the ball 14 is Da, as shown in FIG. 3, L = 2 Da to 5 Da is set. And the convex part 13 stands | starts up from each pocket 12 via the spacing parts 18a and 18b, and the axial direction edge part is formed flat.

また、凸部１３の高さＨは爪片１６ａ，１６ｂの高さと同じであり、半径方向の幅も爪片１６ａ，１６ｂと同じ幅に形成されている。   Further, the height H of the convex portion 13 is the same as the height of the claw pieces 16a and 16b, and the width in the radial direction is also formed to the same width as the claw pieces 16a and 16b.

したがって、保持器２が図２に示す状態に組み込まれて高速回転したとき、凸部１３の平坦面が爪片１６ａ，１６ｂの先端と同じ高さで円周方向に連続することによって、爪片１６ａ，１６ｂだけに特別に撹拌抵抗が発生することがなく、潤滑油の流れを整えることができ、損失トルクを大幅に少なくすることができる。   Therefore, when the cage 2 is assembled in the state shown in FIG. 2 and rotated at a high speed, the flat surface of the convex portion 13 continues in the circumferential direction at the same height as the tips of the claw pieces 16a and 16b. No special stirring resistance is generated only at 16a and 16b, the flow of the lubricating oil can be adjusted, and the loss torque can be greatly reduced.

更に、玉数及びポケット数を減らしてトルク低減を図った場合、ポケット１２どうしの間隔が長くなるが、ポケット１２間には従来のような凹部が連続しておらず、凸部１３が連続しているので、爪片１６ａ，１６ｂの近傍で潤滑油の撹拌が生じることがなく、損失トルクを大幅に少なくすることができる。   Further, when the torque is reduced by reducing the number of balls and the number of pockets, the interval between the pockets 12 becomes longer, but the conventional concave portions are not continuous between the pockets 12, and the convex portions 13 are continuous. Therefore, the lubricating oil is not agitated in the vicinity of the claw pieces 16a and 16b, and the loss torque can be greatly reduced.

玉１４をスナップオン方式でポケット１２内に収納するには、一対の爪片１６ａ，１６ｂが弾性的に開かなければならない。一方、保持器本体１１はプラスチック製であり、爪片１６ａ，１６ｂはもとより、離間部１８ａ，１８ｂ、凸部１３も一体成形されるものである。したがって、成型工程に続く冷却時の収縮により、爪片１６ａ，１６ｂが保持器２の半径方向内方へ倒れることを防止する必要がある。   In order to store the ball 14 in the pocket 12 by the snap-on method, the pair of claw pieces 16a and 16b must be elastically opened. On the other hand, the cage body 11 is made of plastic, and the claw pieces 16a and 16b as well as the separating portions 18a and 18b and the convex portion 13 are integrally formed. Therefore, it is necessary to prevent the claw pieces 16a and 16b from falling inward in the radial direction of the cage 2 due to shrinkage during cooling following the molding process.

仮に、爪片１６ａ，１６ｂが保持器２の半径方向内方に傾いた場合、寸法精度が得られなくなり、玉１４のスナップオンができなくなるばかりか、高速回転時に保持器２の剛性が不足して遠心力による外開きの変形を受けて保持器２が破損する恐れがある。   If the claw pieces 16a and 16b are inclined inward in the radial direction of the cage 2, not only the dimensional accuracy can be obtained and the ball 14 cannot be snapped on, but the rigidity of the cage 2 is insufficient during high-speed rotation. Thus, the cage 2 may be damaged due to deformation of the outward opening due to centrifugal force.

そこで、本実施形態では、このような問題を未然に防止するためと、組み付け時における爪片１６ａ，１６ｂの弾性変形を阻害しないために、離間部１８ａ，１８ｂの底部における最小幅が爪片１６ａ，１６ｂの弾性変形量（（Ｄａ−Ｗ）／２）以上になるように設定されている。このような構成によれば、組み付け時の問題発生を未然に防止できる。   Therefore, in the present embodiment, in order to prevent such a problem and to prevent the elastic deformation of the claw pieces 16a and 16b at the time of assembly, the minimum width at the bottom of the separating portions 18a and 18b is set to the claw piece 16a. , 16b is set to be equal to or greater than the amount of elastic deformation ((Da-W) / 2). According to such a configuration, it is possible to prevent occurrence of problems during assembly.

次に、本発明の第２実施形態を説明する。図５は第２実施形態の保持器の斜視図、図６は第２実施形態の保持器の部分展開図、図７は図６の要部拡大図である。   Next, a second embodiment of the present invention will be described. FIG. 5 is a perspective view of a cage according to the second embodiment, FIG. 6 is a partial development view of the cage according to the second embodiment, and FIG. 7 is an enlarged view of a main part of FIG.

第２実施形態が第１実施形態と異なるのは、離間部２０ａ，２０ｂの構成である。上記のように、離間部２０ａ，２０ｂの底部における最小幅は爪片１６ａ，１６ｂの弾性変形量以上に設定されているが、第２実施形態では離間部２０ａ，２０ｂの幅が第１実施形態よりも狭くなっている。他の構成は、第１実施形態と同じであるので、第１実施形態と同じ構成については図５〜図７に同符号を付しその説明は省略するが、同じ構成による作用効果は第１実施形態と同じである。   The second embodiment differs from the first embodiment in the configuration of the separating portions 20a and 20b. As described above, the minimum width at the bottom of the separation portions 20a and 20b is set to be equal to or greater than the elastic deformation amount of the claw pieces 16a and 16b. In the second embodiment, the width of the separation portions 20a and 20b is the first embodiment. It is narrower than. Since other configurations are the same as those of the first embodiment, the same configurations as those of the first embodiment are denoted by the same reference numerals in FIGS. This is the same as the embodiment.

このように、離間部２０ａ，２０ｂの幅が狭く爪片１６ａ，１６ｂと凸部１３とが近接していることにより、爪片１６ａ，１６ｂと凸部１３とが一体で潤滑油を整流し、爪片１６ａ，１６ｂによる潤滑油の撹拌作用は発生しない。   In this manner, the claw pieces 16a, 16b and the convex portion 13 are close to each other because the width of the separation portions 20a, 20b is narrow, so that the claw pieces 16a, 16b and the convex portion 13 integrally rectify the lubricating oil, The stirring action of the lubricating oil by the claw pieces 16a and 16b does not occur.

なお、離間部２０ａ，２０ｂの幅は、爪片１６ａ，１６ｂの弾性変形に支障を来たさない範囲で狭いほど好ましく、凸部１３による潤滑油の整流作用は第１実施形態よりも第２実施形態の方が優れている。   The width of the spacing portions 20a and 20b is preferably as narrow as possible so as not to hinder the elastic deformation of the claw pieces 16a and 16b, and the rectifying action of the lubricating oil by the convex portion 13 is second than that of the first embodiment. The embodiment is superior.

１ 軸受
２，２２，３１ 保持器
３ 内輪
４ 外輪
１１，３２ 保持器本体
１２，３５ ポケット
１３ 凸部
１４ 玉
１６ａ，１６ｂ，３３ａ，３３ｂ 爪片
１８ａ，１８ｂ，２０ａ，２０ｂ 離間部 DESCRIPTION OF SYMBOLS 1 Bearing 2,22,31 Cage 3 Inner ring 4 Outer ring 11, 32 Cage body 12, 35 Pocket 13 Convex part 14 Balls 16a, 16b, 33a, 33b Claw pieces 18a, 18b, 20a, 20b Separation part

Claims (2)

内輪と、
外輪と、
前記内輪と前記外輪との間に転動自在に配設された複数の玉と、
前記玉を円周方向に沿って所定間隔に保持する複数のポケットが設けられたプラスチック製保持器と、を備えた玉軸受において、
隣接する前記ポケットに保持された玉間距離Ｌが、玉径Ｄａの２倍以上であることを特徴とする玉軸受。 Inner ring,
Outer ring,
A plurality of balls arranged to roll between the inner ring and the outer ring;
In a ball bearing comprising a plastic cage provided with a plurality of pockets for holding the balls at a predetermined interval along the circumferential direction,
A ball bearing characterized in that the distance L between the balls held in the adjacent pockets is at least twice the ball diameter Da. 前記保持器は、
環状の保持器本体と、
前記各ポケットの開口端を構成する一対の爪片と、
前記一対の爪片の円周方向外側に設けられた離間部と、
前記離間部から軸方向に立ち上がり軸方向端部が平坦面を形成し、且つ、軸方向から見て円弧状に形成され、隣接する前記ポケット間に設けられた凸部と、を備え、
前記凸部と前記爪片との前記離間部の底面からの高さは同じ高さに設定されており、
前記凸部と前記爪片との半径方向の幅は同じ幅に設定されていることを特徴とする自動車用トランスミッションに使用される請求項１に記載の玉軸受。
The cage is
An annular cage body;
A pair of claw pieces constituting the open end of each pocket;
A spacing portion provided on the outer circumferential side of the pair of claw pieces;
The rising end in the axial direction from the spaced apart part forms a flat surface, and is formed in an arc shape when viewed from the axial direction, and includes a convex part provided between the adjacent pockets,
The height from the bottom surface of the spacing portion between the convex portion and the claw piece is set to the same height,
2. The ball bearing according to claim 1, wherein the radial width of the convex portion and the claw piece is set to the same width.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012207699A (en) * 2011-03-29 2012-10-25 Nsk Ltd Ball bearing
CN104847790A (en) * 2015-04-15 2015-08-19 中山市鸿程科研技术服务有限公司 Novel bearing
CN113366232A (en) * 2019-01-29 2021-09-07 Ntn株式会社 Ball bearing
CN116517959A (en) * 2023-05-11 2023-08-01 北京理工大学 High-speed lightweight enhanced heat dissipation bearing retainer
WO2023236167A1 (en) * 2022-06-10 2023-12-14 舍弗勒技术股份两合公司 Bearing

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JPH0988968A (en) * 1995-07-21 1997-03-31 Koyo Seiko Co Ltd Cage for ball bearing
JP2000145794A (en) * 1998-11-06 2000-05-26 Mitsubishi Heavy Ind Ltd Ultra-high speed, high rigidity rolling bearing
JP2002122147A (en) * 2000-10-16 2002-04-26 Nsk Ltd Ball bearing, and manufacturing method thereof
JP2004092719A (en) * 2002-08-30 2004-03-25 Nsk Ltd Rolling bearing
JP2006009887A (en) * 2004-06-24 2006-01-12 Nsk Ltd Ball bearing and ball bearing for transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0988968A (en) * 1995-07-21 1997-03-31 Koyo Seiko Co Ltd Cage for ball bearing
JP2000145794A (en) * 1998-11-06 2000-05-26 Mitsubishi Heavy Ind Ltd Ultra-high speed, high rigidity rolling bearing
JP2002122147A (en) * 2000-10-16 2002-04-26 Nsk Ltd Ball bearing, and manufacturing method thereof
JP2004092719A (en) * 2002-08-30 2004-03-25 Nsk Ltd Rolling bearing
JP2006009887A (en) * 2004-06-24 2006-01-12 Nsk Ltd Ball bearing and ball bearing for transmission

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012207699A (en) * 2011-03-29 2012-10-25 Nsk Ltd Ball bearing
CN104847790A (en) * 2015-04-15 2015-08-19 中山市鸿程科研技术服务有限公司 Novel bearing
CN113366232A (en) * 2019-01-29 2021-09-07 Ntn株式会社 Ball bearing
CN113366232B (en) * 2019-01-29 2023-11-17 Ntn株式会社 Ball bearing
WO2023236167A1 (en) * 2022-06-10 2023-12-14 舍弗勒技术股份两合公司 Bearing
CN116517959A (en) * 2023-05-11 2023-08-01 北京理工大学 High-speed lightweight enhanced heat dissipation bearing retainer
CN116517959B (en) * 2023-05-11 2024-01-09 北京理工大学 High-speed lightweight enhanced heat dissipation bearing retainer

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