JP2016056920A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2016056920A
JP2016056920A JP2014185572A JP2014185572A JP2016056920A JP 2016056920 A JP2016056920 A JP 2016056920A JP 2014185572 A JP2014185572 A JP 2014185572A JP 2014185572 A JP2014185572 A JP 2014185572A JP 2016056920 A JP2016056920 A JP 2016056920A
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rolling bearing
annular member
support structure
outer ring
axial direction
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JP6451164B2 (en
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晃嗣 加藤
Akitsugu Kato
晃嗣 加藤
日比　勉
Tsutomu Hibi
勉 日比
田中　進
Susumu Tanaka
進 田中
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NSK Ltd
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  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing which can buffer the axial vibration and impact transmitted to a support structure.SOLUTION: A rolling bearing 1 has an outer ring 3 supported by a support structure 20. Between the outer ring 3 and the support structure 20 in axial direction, a resin annular member 10 is disposed. The annular member 10 has at least one projection 13 projecting in axial direction.SELECTED DRAWING: Figure 5

Description

本発明は転がり軸受に関する。   The present invention relates to a rolling bearing.

従来から、自動車のトランスミッション内においては、歯車支持軸やプーリ支持軸等の回転軸が、玉軸受のような転がり軸受によって、トランスミッションケースやハウジング等の支持構造物に対して回転可能に支持されている。一般的に軸受の固定輪は、支持構造物に直接当接するように、圧入嵌合や隙間嵌合されて組み付けられる。そのため、トランスミッション内の歯車やベルトドライブ機構等のトルク伝達要素から発生する大きな並進荷重や、振動、衝撃、例えば歯車の噛み合い誤差やバックラッシに起因した歯車振動が、トルク伝達軸を介して軸受に伝わる。したがって、このような振動や衝撃が、軸受を介して支持構造物に、ほとんど緩衝されることなくダイレクトに伝わることになる。   Conventionally, in automobile transmissions, rotating shafts such as gear support shafts and pulley support shafts are rotatably supported with respect to support structures such as transmission cases and housings by rolling bearings such as ball bearings. Yes. Generally, the fixed ring of the bearing is assembled by press-fitting or clearance fitting so as to directly contact the support structure. For this reason, large translational loads generated from torque transmission elements such as gears in the transmission and belt drive mechanisms, vibrations and shocks, for example, gear meshing errors due to gear meshing errors and backlash, are transmitted to the bearing via the torque transmission shaft. . Therefore, such vibrations and impacts are directly transmitted to the support structure through the bearings with almost no buffering.

また、ベルト式無段変速機においては、入力回転軸に伝達された動力は、駆動側プーリから金属ベルトを介して従動側プーリに伝達されるが、ベルトを構成するエレメント（コマ）による高周波領域の振動が作用する。近年、振動レベルはやや悪化傾向であり、何れも車両の低騒音化が大きな課題となっている。   In the belt type continuously variable transmission, the power transmitted to the input rotating shaft is transmitted from the driving pulley to the driven pulley via the metal belt, but the high frequency region by the elements (coma) constituting the belt. The vibration of acts. In recent years, the vibration level is slightly worsening, and in all cases, the reduction of vehicle noise has become a major issue.

さらに、トランスミッションケースはアルミダイカスト等で形成された薄肉構造となっていることが一般的であり、トランスミッション内で発生した振動や衝撃が、ダイレクトに伝わった場合には、ケース固有の振動モードが励起され、特にその方向が面直方向、いわゆる軸受のアキシャル方向（軸方向）の振動や衝撃が入力された場合には、ケースから放射音となってユーザーに不快な音として伝達される。   In addition, transmission cases generally have a thin-walled structure formed of aluminum die-casting, etc. When vibrations and impacts generated in the transmission are transmitted directly, the vibration mode specific to the case is excited. In particular, when vibration or impact in the direction perpendicular to the surface, that is, the axial direction (axial direction) of the bearing is input, the sound is emitted from the case and transmitted to the user as an unpleasant sound.

ここで、特許文献１〜３には、防振機能を有する軸受構造が開示されている。より詳細に、特許文献１には、支持構造物と、第１レース、第２レース、複数のころ部材、及び保持器を含むスラストころ軸受と、の間に振動絶縁体が配置されることが記載されている。また、特許文献２には、回転軸を支持する鋼製軸受と軽合金製ケースとの間に介在させている従来の鋼鈑製シムの一部若しくはすべてを、制振性を有する樹脂製シムに置き換えることが記載されている。また、特許文献３には、外輪の外周面に防振部材が設けられている防振型転がり軸受において、防振部材が、外輪の外周面および軸方向両端面を覆う鍔付き円筒形に成形されているとともに周方向に複数の窓孔を有する芯金と、この芯金の窓孔に充填されるとともに、芯金の鍔部分を含む芯金全体に被着される弾性体と、から構成されることが記載されている。   Here, Patent Documents 1 to 3 disclose a bearing structure having a vibration isolation function. More specifically, in Patent Document 1, a vibration insulator is disposed between a support structure and a thrust roller bearing including a first race, a second race, a plurality of roller members, and a cage. Have been described. Further, Patent Document 2 discloses that a resin shim having vibration damping properties is used for a part or all of a conventional steel-steel shim interposed between a steel bearing supporting a rotating shaft and a light alloy case. It is described that it is replaced with. Further, in Patent Document 3, in a vibration-proof type rolling bearing in which a vibration-proof member is provided on the outer peripheral surface of the outer ring, the vibration-proof member is formed into a flanged cylindrical shape that covers the outer peripheral surface and both axial end surfaces of the outer ring. And a cored bar having a plurality of window holes in the circumferential direction, and an elastic body that fills the windowed hole of the cored bar and is attached to the entire cored bar including the flange part of the cored bar. It is described that it is done.

特開２０１２−９７８９８号公報JP 2012-97898 A 特開平７−１４５８１４号公報JP-A-7-145814 特開平８−９３７５９号公報JP-A-8-93759

しかしながら、特許文献１には、実使用時に負荷されるアキシャル荷重による耐久性については言及されていない。また、特許文献２には、高アキシャル荷重負荷時の耐久性や、クリープが発生した場合の耐久性について言及がされていない。また、特許文献３の軸受では、高温環境下の耐久性及びクリープに対する課題が存在する。   However, Patent Document 1 does not mention durability due to an axial load applied during actual use. In addition, Patent Document 2 does not mention durability when a high axial load is applied and durability when creep occurs. Moreover, in the bearing of patent document 3, the subject with respect to durability in a high temperature environment and creep exists.

本発明は上記事情に鑑みてなされたものであり、支持構造物に伝達される軸方向の振動や衝撃を緩衝することが可能な転がり軸受を提供することを目的とする。   The present invention has been made in view of the above circumstances, and an object thereof is to provide a rolling bearing capable of buffering axial vibration and impact transmitted to a support structure.

本発明の上記目的は、下記の構成により達成される。
（１） 固定輪が支持構造物に支持される転がり軸受であって、
前記固定輪と前記支持構造物との軸方向における間には、樹脂製の環状部材が配置され、
前記環状部材は、軸方向に突出する突起部を少なくとも一つ有する
ことを特徴とする転がり軸受。
（２） 前記突起部は、断面形状が台形形状又は半円形状である
ことを特徴とする（１）に記載の転がり軸受。
（３） 前記台形形状は、上底の寸法が、下底の寸法の１／２以下である
ことを特徴とする（２）に記載の転がり軸受。
（４） 前記固定輪の径方向における最小肉厚をｈとし、
前記固定輪と回転輪との間に転動自在に配置される転動体の直径をＤａとしたとき、
０．４Ｄａ≦ｈ≦０．８Ｄａを満たす
ことを特徴とする（１）〜（３）の何れか１つに記載の転がり軸受。
（５） トランスミッション内の回転軸支持用途に用いられる
ことを特徴とする（１）〜（４）の何れか１つに記載の転がり軸受。 The above object of the present invention can be achieved by the following constitution.
(1) A rolling bearing in which a fixed ring is supported by a support structure,
Between the fixed ring and the support structure in the axial direction, a resin annular member is disposed,
The annular member has at least one protrusion protruding in the axial direction.
(2) The rolling bearing according to (1), wherein the protrusion has a trapezoidal shape or a semicircular shape in cross section.
(3) The rolling bearing according to (2), wherein the trapezoidal shape has an upper base dimension that is ½ or less of a lower base dimension.
(4) The minimum thickness in the radial direction of the fixed ring is h,
When the diameter of the rolling element that is freely rollable between the fixed wheel and the rotating wheel is Da,
The rolling bearing according to any one of (1) to (3), wherein 0.4 Da ≦ h ≦ 0.8 Da is satisfied.
(5) The rolling bearing according to any one of (1) to (4), which is used for supporting a rotating shaft in a transmission.

本発明の転がり軸受によれば、固定輪と支持構造物との軸方向における間には樹脂製の環状部材が配置され、環状部材は軸方向に突出する突起部を少なくとも一つ有する。したがって、歯車やベルト等によるトルク伝達採用に起因して回転軸上に発生する軸方向振動や衝撃が、転がり軸受を介して支持構造物に伝達される際に、環状部材の突起部が撓むことによる緩衝効果が発現する。これにより、発音体となり易いトランスミッションケース等の支持構造物の周辺構造の振動が抑制され、トランスミッション等の装置の騒音低減が実現できる。   According to the rolling bearing of the present invention, the resin-made annular member is disposed between the fixed ring and the support structure in the axial direction, and the annular member has at least one protrusion protruding in the axial direction. Therefore, when the axial vibration or impact generated on the rotating shaft due to the adoption of torque transmission by a gear or a belt is transmitted to the support structure via the rolling bearing, the protrusion of the annular member bends. A buffering effect is exhibited. Thereby, the vibration of the peripheral structure of the support structure such as a transmission case that is likely to be a sounding body is suppressed, and noise reduction of a device such as a transmission can be realized.

円周方向から見た実施形態に係る転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing which concerns on embodiment seen from the circumferential direction. 径方向から見た環状部材の一部断面図である。It is a partial cross section figure of the annular member seen from radial direction. 軸方向から見た環状部材の一部平面図である。It is a partial top view of the annular member seen from the axial direction. 軸方向から見た環状部材の一部平面図である。It is a partial top view of the annular member seen from the axial direction. 支持構造物に支持された転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing supported by the support structure. 変形例に係る転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing which concerns on a modification. 環状部材が固定された図６の転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing of FIG. 6 to which the annular member was fixed. 変形例に係る転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing which concerns on a modification. 環状部材が固定された図８の転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing of FIG. 8 to which the annular member was fixed. 芯金によって環状部材が固定された転がり軸受の一部断面図である。It is a partial cross section figure of the rolling bearing by which the annular member was fixed with the metal core. （ａ）は軸方向から見た変形例に係る転がり軸受の平面図であり、（ｂ）は（ａ）のＸＩ−ＸＩ断面図である。(A) is a top view of the rolling bearing which concerns on the modification seen from the axial direction, (b) is XI-XI sectional drawing of (a).

以下、本発明の実施形態に係る転がり軸受について、図面を用いて説明する。   Hereinafter, a rolling bearing 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１は、固定輪である外輪３と、回転輪である内輪５と、外輪３と内輪５との間に転動自在に配置される複数の玉７（転動体）と、を備える玉軸受である。外輪３の軸方向一端面３ａ（図１中、左端面）には、樹脂製の環状部材１０が配置される (First embodiment)
As shown in FIG. 1, the rolling bearing 1 of the present embodiment includes a plurality of outer rings 3 that are fixed rings, an inner ring 5 that is a rotating ring, and a plurality of rolls that are arranged between the outer ring 3 and the inner ring 5 so as to be freely rollable. A ball bearing provided with balls 7 (rolling elements). An annular member 10 made of resin is disposed on one end surface 3a in the axial direction of the outer ring 3 (left end surface in FIG. 1).

環状部材１０の樹脂材料としては、例えば、比較的安価でトランスミッション用潤滑油で実績がある４６ナイロンが用いられる。また、環状部材１０は、外輪３の軸方向一端面３ａに当接する円環状基部１１と、円環状基部１１から軸方向に突出する複数の突起部１３と、を有する。   As the resin material of the annular member 10, for example, 46 nylon, which is relatively inexpensive and has a proven record in transmission lubricating oil, is used. The annular member 10 includes an annular base portion 11 that abuts on the one axial end surface 3 a of the outer ring 3, and a plurality of protrusions 13 that protrude from the annular base portion 11 in the axial direction.

突起部１３の形状は特に限定されないが、後述する支持構造物２０（図５参照）と当接する際に撓みが生じ易い形状とすることが好ましい。例えば、図２又は図３に示すように、突起部１３は四角錐台形状、すなわち断面形状を台形形状としても良い。図示の例では、円周方向に等間隔で配置された複数の突起部１３が、径方向に三列に亘って形成されている。このとき、突起部１３の断面形状の台形形状は、上底の寸法Ａが下底の寸法Ｂの１／２以下（Ａ≦Ｂ／２）に設定される。また、突起部１３の四角錐台を構成する二枚の平行な上下台形面の面積比は、１０〜２５％に設定される。これにより、アキシャル荷重を受けたときの突起部１３の変位量が大きくなり、後述する支持構造物２０に伝達される荷重を緩衝する効果を高めることが可能となる。   Although the shape of the protrusion part 13 is not specifically limited, It is preferable to set it as the shape which is easy to produce bending when contacting the support structure 20 (refer FIG. 5) mentioned later. For example, as shown in FIG. 2 or FIG. 3, the protrusion 13 may have a quadrangular pyramid shape, that is, the cross-sectional shape may be a trapezoidal shape. In the illustrated example, a plurality of protrusions 13 arranged at equal intervals in the circumferential direction are formed in three rows in the radial direction. At this time, the trapezoidal shape of the cross-sectional shape of the protrusion 13 is set such that the dimension A of the upper base is equal to or less than ½ of the dimension B of the lower base (A ≦ B / 2). In addition, the area ratio of the two parallel upper and lower trapezoidal surfaces constituting the quadrangular frustum of the protrusion 13 is set to 10 to 25%. Thereby, the amount of displacement of the protrusion 13 when receiving an axial load is increased, and the effect of buffering the load transmitted to the support structure 20 described later can be enhanced.

突起部１３は、図４に示すように、半球形状、すなわち断面形状を半円形状としても良い。図示の例では、円周方向に等間隔で配置された複数の突起部１３が、径方向に三列に亘って形成されている。ここで、三列のうち、二列目の突起部１３は、一列目及び三列目の突起部１３に対して、円周方向に突起部１３の１／２個分、位相をずらして配置されている。これにより、円環状基部１１により多くの突起部１３を配置することを可能としている。このように突起部１３の断面形状を半円形状とすることで、微小荷重時において、突起部１３と支持構造物２０との接触が点接触となるため、突起部１３の変位量が大きくなり防振効果を高めることが可能である。   As shown in FIG. 4, the protrusion 13 may have a hemispherical shape, that is, a cross-sectional shape that is a semicircular shape. In the illustrated example, a plurality of protrusions 13 arranged at equal intervals in the circumferential direction are formed in three rows in the radial direction. Here, of the three rows, the projections 13 in the second row are arranged with a phase shifted by 1/2 of the projections 13 in the circumferential direction with respect to the projections 13 in the first row and the third row. Has been. Thereby, it is possible to arrange more protrusions 13 on the annular base 11. Thus, by making the cross-sectional shape of the protruding portion 13 a semicircular shape, the contact between the protruding portion 13 and the support structure 20 becomes a point contact at the time of a minute load, so that the displacement amount of the protruding portion 13 increases. It is possible to enhance the anti-vibration effect.

このように構成された転がり軸受１は、図５に示すように、トランスミッションケースやハウジング等の支持構造物２０に支持される。ここで、支持構造物２０の内周面２１には径方向に突出する内周側凸部２３が形成される。そして、支持構造物２０の内周面２１に、環状部材１０及び転がり軸受１を軸方向から挿入し、環状部材１０と支持構造物２０の内周側凸部２３とを当接させる。さらに、外輪３の軸方向他端面３ｂに当接する環状の固定部材２５を、ボルト等の螺合部材２７によって、支持構造物２０に固定する。したがって、固定部材２５は、外輪３を支持構造物２０の内周側凸部２３側に向かって押圧する。これにより、環状部材１０は、外輪３と支持構造物２０の内周側凸部２３との軸方向における間に確実に固定される。なお、回転輪である内輪５は、トランスミッション内の歯車支持軸やプーリ支持軸等の回転軸の外周に固定される。   As shown in FIG. 5, the rolling bearing 1 configured as described above is supported by a support structure 20 such as a transmission case or a housing. Here, the inner peripheral surface 21 of the support structure 20 is formed with an inner peripheral convex portion 23 protruding in the radial direction. Then, the annular member 10 and the rolling bearing 1 are inserted into the inner peripheral surface 21 of the support structure 20 from the axial direction, and the annular member 10 and the inner peripheral convex portion 23 of the support structure 20 are brought into contact with each other. Further, an annular fixing member 25 that abuts against the other axial end surface 3b of the outer ring 3 is fixed to the support structure 20 by a screwing member 27 such as a bolt. Therefore, the fixing member 25 presses the outer ring 3 toward the inner peripheral convex portion 23 side of the support structure 20. Thereby, the annular member 10 is reliably fixed between the outer ring 3 and the inner peripheral convex portion 23 of the support structure 20 in the axial direction. The inner ring 5 which is a rotating wheel is fixed to the outer periphery of a rotating shaft such as a gear support shaft or a pulley support shaft in the transmission.

なお、上述のように支持構造物２０に固定する前に、環状部材１０と外輪３とは予め接着等によって一体化しておくことが好ましい。環状部材１０と転がり軸受１との一体化によって、部品点数を減らし、組付時の負荷やセットミス等を軽減できる。また、接着以外にも、図６〜９に示すように環状部材１０を外輪３の内周面又は外周面に圧入することにより一体化してもよい。   In addition, before fixing to the support structure 20 as mentioned above, it is preferable that the annular member 10 and the outer ring 3 are integrated in advance by bonding or the like. By integrating the annular member 10 and the rolling bearing 1, the number of parts can be reduced, and a load and a setting error at the time of assembly can be reduced. In addition to bonding, the annular member 10 may be integrated by being press-fitted into the inner peripheral surface or outer peripheral surface of the outer ring 3 as shown in FIGS.

より詳細に、環状部材１０を外輪３の内周面に圧入固定する場合には、図６に示すように、外輪３の内周面に内周溝３ｃを形成する。また、図７に示すように、環状部材１０は断面略Ｌ字形状とされ、円環状基部１１の径方向内側端部から軸方向に延出する内側鍔部１５が形成される。そして、内側鍔部１５を外輪３の内周面に圧入すると共に、内側鍔部１５に形成した嵌合凸部１５ａを外輪３の内周溝３ｃに嵌合することにより、環状部材１０を外輪３に確実に固定する。   More specifically, when the annular member 10 is press-fitted and fixed to the inner peripheral surface of the outer ring 3, an inner peripheral groove 3c is formed on the inner peripheral surface of the outer ring 3, as shown in FIG. Further, as shown in FIG. 7, the annular member 10 has a substantially L-shaped cross section, and an inner flange 15 extending in the axial direction from the radially inner end of the annular base 11 is formed. Then, the inner flange 15 is press-fitted into the inner peripheral surface of the outer ring 3, and the fitting member 15 a formed on the inner flange 15 is fitted into the inner circumferential groove 3 c of the outer ring 3, whereby the annular member 10 is Secure to 3

また、環状部材１０を外輪３の外周面に圧入固定する場合には、図８に示すように、外輪３の外周面に外周溝３ｄを形成する。なお、図示の例では、外周溝３ｄは一対形成されている。また、図９に示すように、環状部材１０は断面略Ｌ字形状とされ、円環状基部１１の径方向外側端部から軸方向に延出する外側鍔部１７が形成される。そして、外側鍔部１７を外輪３の外周面に圧入すると共に、外側鍔部１７に形成した一対の嵌合凸部１７ａを外輪３の外周溝３ｄに嵌合することにより、環状部材１０を外輪３に確実に固定する。   When the annular member 10 is press-fitted and fixed to the outer peripheral surface of the outer ring 3, an outer peripheral groove 3 d is formed on the outer peripheral surface of the outer ring 3 as shown in FIG. 8. In the illustrated example, a pair of outer peripheral grooves 3d are formed. Further, as shown in FIG. 9, the annular member 10 has a substantially L-shaped cross section, and is formed with an outer flange 17 that extends in the axial direction from the radially outer end of the annular base 11. Then, the outer flange portion 17 is press-fitted into the outer peripheral surface of the outer ring 3, and the pair of fitting convex portions 17 a formed on the outer flange portion 17 are fitted into the outer peripheral groove 3 d of the outer ring 3, whereby the annular member 10 is Secure to 3

また、環状部材１０に覆われた断面略Ｌ字形状の芯金３０を、外輪３の内周面又は外周面に圧入することにより、環状部材１０を外輪３に固定しても構わない。なお、図１０には、芯金３０が外輪３の内周面に圧入された状態が示されている。   Further, the annular member 10 may be fixed to the outer ring 3 by press-fitting a core metal 30 having a substantially L-shaped cross section covered with the annular member 10 into the inner peripheral surface or the outer peripheral surface of the outer ring 3. 10 shows a state in which the core 30 is press-fitted into the inner peripheral surface of the outer ring 3.

このように、図６〜１０に示した何れの構成であっても、環状部材１０と外輪３（転がり軸受１）とが一体となるような構成とすることで、トランスミッション等への組付時の製品取扱いが容易となり、組付時の負荷やセットミスを軽減できる。   As described above, in any of the configurations shown in FIGS. 6 to 10, the annular member 10 and the outer ring 3 (rolling bearing 1) are integrated so as to be assembled to a transmission or the like. The product can be handled easily, reducing the load and setting errors during assembly.

さらに、図１１に示すように、外輪３の軸方向両側から、それぞれ環状部材１０に覆われた一対の芯金３０を圧入固定することによって、外輪３の軸方向両側に環状部材１０を配置しても構わない。この場合、転がり軸受１は軸方向両側のアキシャル方向荷重に対する緩衝機能を有するので、より幅広い適用性が期待できる。   Furthermore, as shown in FIG. 11, the annular members 10 are arranged on both sides in the axial direction of the outer ring 3 by press-fitting and fixing a pair of core bars 30 covered with the annular members 10 from both sides in the axial direction of the outer ring 3. It doesn't matter. In this case, since the rolling bearing 1 has a buffering function with respect to axial loads on both sides in the axial direction, wider applicability can be expected.

以上説明したように、本実施形態の転がり軸受１によれば、外輪３と支持構造物２０との軸方向における間には樹脂製の環状部材１０が配置され、環状部材１０は軸方向に突出する突起部１３を少なくとも一つ有する。したがって、歯車やベルト等によるトルク伝達採用に起因して回転軸上に発生する軸方向振動や衝撃が、転がり軸受１を介して支持構造物２０に伝達される際に、環状部材１０の突起部１３が撓むことによる緩衝効果が発現する。これにより、発音体となり易いトランスミッションケース等の支持構造物２０の周辺構造の振動が抑制され、トランスミッション等の装置の騒音低減が実現できる。   As described above, according to the rolling bearing 1 of the present embodiment, the resin-made annular member 10 is disposed between the outer ring 3 and the support structure 20 in the axial direction, and the annular member 10 projects in the axial direction. At least one protrusion 13 is provided. Therefore, when the axial vibration or impact generated on the rotating shaft due to the adoption of torque transmission by a gear, a belt, or the like is transmitted to the support structure 20 via the rolling bearing 1, the protruding portion of the annular member 10. A buffering effect due to the bending of 13 appears. Thereby, the vibration of the peripheral structure of the support structure 20 such as a transmission case that is likely to be a sounding body is suppressed, and noise reduction of a device such as a transmission can be realized.

なお、外輪３と支持構造物２０との間でクリープが発生した場合、環状部材１０の摩耗や、環状部材１０と外輪３との間の波打ち現象の発生が懸念されるが、外輪３の径方向肉厚及び軸方向幅を適正化することにより、クリープを抑制し、防振機能を損なわないように設定している。具体的には、外輪３の径方向における最小肉厚をｈとし、玉７の直径をＤａとしたとき、０．４Ｄａ≦ｈ≦０．８Ｄａを満たすように設定される。仮に０．４Ｄａ＞ｈである場合、外輪３の剛性が不足することにより、重荷重時に外輪３及び環状部材１０が波打ち状に変形し、外輪３と支持構造物２０との間でクリープが発生する可能性がある。また、ｈ＞０．８Ｄａである場合、外輪３の外径寸法が過度に大きくなり、装置の大型化や重量増大を招いてしまう。   In addition, when creep occurs between the outer ring 3 and the support structure 20, there is a concern about wear of the annular member 10 and occurrence of a wavy phenomenon between the annular member 10 and the outer ring 3. By optimizing the directional thickness and the axial width, creep is suppressed and the vibration-proof function is not impaired. Specifically, when the minimum thickness in the radial direction of the outer ring 3 is h and the diameter of the ball 7 is Da, it is set to satisfy 0.4 Da ≦ h ≦ 0.8 Da. If 0.4 Da> h, the rigidity of the outer ring 3 is insufficient, so that the outer ring 3 and the annular member 10 are deformed in a wavy shape under heavy load, and creep occurs between the outer ring 3 and the support structure 20. there's a possibility that. Moreover, when h> 0.8 Da, the outer diameter of the outer ring 3 becomes excessively large, leading to an increase in size and weight of the device.

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.

例えば、上述の実施形態では、固定輪として外輪３を、回転輪として内輪５を適用したが、逆に、回転輪として外輪３を、固定輪として内輪５を適用しても構わない。この場合、内輪５が支持構造物に支持され、内輪５と当該支持構造物との軸方向における間に環状部材１０が配置される。   For example, in the above-described embodiment, the outer ring 3 is applied as a fixed ring and the inner ring 5 is applied as a rotating ring. Conversely, the outer ring 3 may be applied as a rotating ring and the inner ring 5 may be applied as a fixed ring. In this case, the inner ring 5 is supported by the support structure, and the annular member 10 is disposed between the inner ring 5 and the support structure in the axial direction.

１ 転がり軸受
３ 外輪（固定輪）
３ａ 軸方向一端面
３ｂ 軸方向他端面
３ｃ 内周溝
３ｄ 外周溝
５ 内輪（回転輪）
７ 玉（転動体）
１０ 環状部材
１１ 円環状基部
１３ 突起部
１５ 内側鍔部
１５ａ 嵌合凸部
１７ 外側鍔部
１７ａ 嵌合凸部
２０ 支持構造物
２１ 内周面
２３ 内周側凸部
２５ 固定部材
２７ 螺合部材
３０ 芯金 1 Rolling bearing 3 Outer ring (fixed ring)
3a Axial end surface 3b Axial other end surface 3c Inner circumferential groove 3d Outer circumferential groove 5 Inner ring (rotating ring)
7 balls (rolling elements)
DESCRIPTION OF SYMBOLS 10 Ring member 11 Circular base part 13 Protrusion part 15 Inner collar part 15a Fitting convex part 17 Outer collar part 17a Fitting convex part 20 Support structure 21 Inner peripheral surface 23 Inner peripheral side convex part 25 Fixing member 27 Screwing member 30 Cored bar

Claims (5)

固定輪が支持構造物に支持される転がり軸受であって、
前記固定輪と前記支持構造物との軸方向における間には、樹脂製の環状部材が配置され、
前記環状部材は、軸方向に突出する突起部を少なくとも一つ有する
ことを特徴とする転がり軸受。 A rolling bearing in which a fixed ring is supported by a support structure,
Between the fixed ring and the support structure in the axial direction, a resin annular member is disposed,
The annular member has at least one protrusion protruding in the axial direction. 前記突起部は、断面形状が台形形状又は半円形状である
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 the protrusion has a trapezoidal shape or a semicircular shape in cross section. 前記台形形状は、上底の寸法が、下底の寸法の１／２以下である
ことを特徴とする請求項２に記載の転がり軸受。 The rolling bearing according to claim 2, wherein the trapezoidal shape has an upper base dimension that is ½ or less of a lower base dimension. 前記固定輪の径方向における最小肉厚をｈとし、
前記固定輪と回転輪との間に転動自在に配置される転動体の直径をＤａとしたとき、
０．４Ｄａ≦ｈ≦０．８Ｄａを満たす
ことを特徴とする請求項１〜３の何れか１項に記載の転がり軸受。 The minimum thickness in the radial direction of the fixed ring is h,
When the diameter of the rolling element that is freely rollable between the fixed wheel and the rotating wheel is Da,
The rolling bearing according to claim 1, wherein 0.4 Da ≦ h ≦ 0.8 Da is satisfied. トランスミッション内の回転軸支持用途に用いられる
ことを特徴とする請求項１〜４の何れか１項に記載の転がり軸受。 It is used for the rotating shaft support use in a transmission, The rolling bearing of any one of Claims 1-4 characterized by the above-mentioned.
JP2014185572A 2014-09-11 2014-09-11 Rolling bearing Expired - Fee Related JP6451164B2 (en)

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