JP2014228079A - Rolling bearing - Google Patents

Rolling bearing Download PDF

Info

Publication number
JP2014228079A
JP2014228079A JP2013109060A JP2013109060A JP2014228079A JP 2014228079 A JP2014228079 A JP 2014228079A JP 2013109060 A JP2013109060 A JP 2013109060A JP 2013109060 A JP2013109060 A JP 2013109060A JP 2014228079 A JP2014228079 A JP 2014228079A
Authority
JP
Japan
Prior art keywords
outer ring
load
rolling bearing
bearing
annular groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2013109060A
Other languages
Japanese (ja)
Other versions
JP6064783B2 (en
Inventor
智 茂木
Satoshi Mogi
智 茂木
田中　進
Susumu Tanaka
進 田中
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2013109060A priority Critical patent/JP6064783B2/en
Publication of JP2014228079A publication Critical patent/JP2014228079A/en
Application granted granted Critical
Publication of JP6064783B2 publication Critical patent/JP6064783B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing that can prevent occurrence of creep on the outer peripheral surface of an outer ring even in a case of being used under oil lubrication or grease lubrication and under a heavy load condition or a rotation load or light load condition.SOLUTION: At least one annular groove 15 is formed over a whole outer peripheral surface 11b of an outer ring 11 of a rolling bearing 10, and an annular elastic body 16 for preventing occurrence of creep is mounted on the annular groove 15. When the radial minimum wall thickness of the outer ring 11 is defined as h1, the minimum wall thickness between the annular groove 15 and an outer ring raceway surface 11a is defined as h2, the diameter of a rolling body 13 is defined as Da, a bearing load is defined as P, and a basic dynamic load rating is defined as Cr, the following relations are satisfied: 0.29(P/Cr)+0.26≤h1/Da≤0.8, and 0.29(P/Cr)+0.26≤h2/Da≤0.8.

Description

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

ハイブリッド・トランスミッションや電気自動車に搭載されるモータの回転軸を回転自在に支持する転がり軸受においては、オイル潤滑又はグリース潤滑で、回転荷重や軽荷重条件下で使用されると、ハウジングと外輪が隙間嵌めの場合は、外輪の外周面でクリープが発生する可能性があり、外輪の外周面とハウジングの内周面との間にＯリングなどの環状弾性体を配置して、クリープの発生を防止している。そして、その具体例としては、外輪の外周面に環状溝を形成すると共に、その環状溝に楕円形状又は多角形状のＯリングを装着するものが知られる（例えば、特許文献１参照）。   In rolling bearings that rotatably support the rotating shaft of a motor mounted on a hybrid transmission or an electric vehicle, the housing and the outer ring have a clearance when used under rotational or light load conditions with oil lubrication or grease lubrication. In the case of fitting, creep may occur on the outer peripheral surface of the outer ring. An annular elastic body such as an O-ring is placed between the outer peripheral surface of the outer ring and the inner peripheral surface of the housing to prevent creep. doing. As a specific example, an annular groove is formed on the outer peripheral surface of the outer ring, and an elliptical or polygonal O-ring is attached to the annular groove (see, for example, Patent Document 1).

また、その一方で、トランスミッションの減速機のギヤを支持する転がり軸受のように、一方向からの荷重を受けながら使用される転がり軸受の場合、重荷重条件下では、外輪の外周面が波打ち変形することにより外輪の外周面でクリープが発生するため、外輪の肉厚及び幅を増すなどして剛性を高めて、その波打ち変形を抑制する対策が一般的に知られている。   On the other hand, in the case of a rolling bearing that is used while receiving a load from one direction, such as a rolling bearing that supports the gear of a reduction gear of the transmission, the outer peripheral surface of the outer ring is wavyly deformed under heavy load conditions. As a result, creep occurs on the outer peripheral surface of the outer ring. Therefore, a countermeasure for increasing the rigidity by increasing the thickness and width of the outer ring and suppressing the wavy deformation is generally known.

特開２００８−１５７３９６号公報JP 2008-157396 A

しかしながら、近年では、モータの回転軸を支持する軸受のように、回転荷重を受けると共に、ギヤの反力のような大きな荷重まで受ける使われ方が増えてきており、上述した２つの対策のうちの一方のみでは、クリープの発生を効果的に防止できなかった。また、上記特許文献１に記載の転がり軸受では、重荷重条件下におけるクリープ対策については触れられていなかった。   However, in recent years, the use of receiving a rotational load and a large load such as a reaction force of a gear has been increasing like a bearing that supports a rotating shaft of a motor. Only one of these could not effectively prevent the occurrence of creep. Further, in the rolling bearing described in Patent Document 1, the countermeasure against creep under heavy load conditions has not been mentioned.

本発明は、前述の事情に鑑みてなされたものであり、その目的は、オイル潤滑又はグリース潤滑下で、重荷重条件や、回転荷重又は軽荷重条件下で使用されたとしても、外輪の外周面でのクリープの発生を防止す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 view of the above-described circumstances, and its purpose is to provide an outer periphery of an outer ring even when used under heavy load conditions, rotational loads, or light load conditions under oil lubrication or grease lubrication. An object of the present invention is to provide a rolling bearing capable of preventing the occurrence of creep on the surface.

本発明の上記目的は、下記の構成により達成される。
（１）内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、外輪軌道面と内輪軌道面との間に転動自在に配置される複数の転動体と、を備え、外輪の外周面に、少なくとも１つの環状溝が全周に亘って形成され、環状溝に、クリープの発生を防止するための環状弾性体が装着される転がり軸受であって、外輪の径方向最小肉厚をｈ１、環状溝と外輪軌道面との間の最小肉厚をｈ２、転動体の直径をＤａ、軸受荷重をＰ、基本動定格荷重をＣｒとした場合において、０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ１／Ｄａ≦０．８、且つ０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ２／Ｄａ≦０．８を満たすように設定されることを特徴とする転がり軸受。
（２）内輪にアキシアル荷重を含む重荷重が負荷され、内輪から転動体を介して外輪にアキシアル荷重が伝達される状態において、環状溝は、軸受中心を通り軸受端面に平行な軸方向中心線よりもアキシアル荷重を受けていない側に形成されることを特徴とする（１）に記載の転がり軸受。
（３）ハイブリッド・トランスミッション又は電気自動車に搭載されるモータの回転軸を支持するために使用されることを特徴とする（１）又は（２）に記載の転がり軸受。 The above object of the present invention can be achieved by the following constitution.
(1) An outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rolling elements arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface; A rolling bearing in which at least one annular groove is formed on the outer peripheral surface of the outer ring over the entire circumference, and an annular elastic body for preventing the occurrence of creep is attached to the annular groove. When the minimum radial thickness is h1, the minimum thickness between the annular groove and the outer raceway surface is h2, the diameter of the rolling element is Da, the bearing load is P, and the basic dynamic load rating is Cr, 0.29 (P / Cr) + 0.26 ≦ h1 / Da ≦ 0.8 and 0.29 (P / Cr) + 0.26 ≦ h2 / Da ≦ 0.8 Rolling bearing.
(2) In a state where a heavy load including an axial load is applied to the inner ring and the axial load is transmitted from the inner ring to the outer ring via the rolling elements, the annular groove passes through the center of the bearing and is parallel to the bearing end surface. The rolling bearing according to (1), wherein the rolling bearing is formed on a side not receiving an axial load.
(3) The rolling bearing according to (1) or (2), which is used for supporting a rotating shaft of a motor mounted on a hybrid transmission or an electric vehicle.

本発明の転がり軸受によれば、外輪の径方向最小肉厚をｈ１、環状溝と外輪軌道面との間の最小肉厚をｈ２、転動体の直径をＤａ、軸受荷重をＰ、基本動定格荷重をＣｒとした場合において、０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ１／Ｄａ≦０．８、且つ０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ２／Ｄａ≦０．８を満たすように設定されるため、外輪の径方向最小肉厚ｈ１及び環状溝と外輪軌道面との間の最小肉厚ｈ２を適正化して、外輪の外周面の波打ち変形を抑制することができる。これにより、オイル潤滑又はグリース潤滑下で、重荷重条件や、回転荷重又は軽荷重条件下で軸受が使用されたとしても、外輪の外周面でのクリープの発生を防止することができる。   According to the rolling bearing of the present invention, the minimum radial thickness of the outer ring is h1, the minimum thickness between the annular groove and the outer ring raceway surface is h2, the diameter of the rolling element is Da, the bearing load is P, the basic dynamic rating. When the load is Cr, 0.29 · (P / Cr) + 0.26 ≦ h1 / Da ≦ 0.8 and 0.29 · (P / Cr) + 0.26 ≦ h2 / Da ≦ 0.8 Therefore, it is possible to optimize the minimum radial thickness h1 of the outer ring and the minimum thickness h2 between the annular groove and the outer ring raceway surface, thereby suppressing the wavy deformation of the outer peripheral surface of the outer ring. . Accordingly, even when the bearing is used under heavy load conditions, rotational loads, or light load conditions under oil lubrication or grease lubrication, the occurrence of creep on the outer peripheral surface of the outer ring can be prevented.

本発明に係る転がり軸受の第１実施形態を説明する要部断面図である。It is principal part sectional drawing explaining 1st Embodiment of the rolling bearing which concerns on this invention. 本発明に係る転がり軸受の第２実施形態を説明する要部断面図である。It is principal part sectional drawing explaining 2nd Embodiment of the rolling bearing which concerns on this invention.

以下、本発明に係る転がり軸受の各実施形態について、図面に基づいて詳細に説明する。なお、以下の説明において、「軸受中心」とは、外輪及び内輪の両軌道面を基準にした中心位置である。   Hereinafter, each embodiment of the rolling bearing which concerns on this invention is described in detail based on drawing. In the following description, the “bearing center” is a center position based on both raceways of the outer ring and the inner ring.

（第１実施形態）
まず、図１を参照して、本発明に係る転がり軸受の第１実施形態について説明する。 (First embodiment)
First, a first embodiment of a rolling bearing according to the present invention will be described with reference to FIG.

本実施形態の転がり軸受１０は、図１に示すように、内周面に外輪軌道面１１ａを有する外輪１１と、外周面に内輪軌道面１２ａを有する内輪１２と、外輪軌道面１１ａと内輪軌道面１２ａとの間に転動可能に配設される複数の玉（転動体）１３と、複数の玉１３を円周方向に等間隔に保持する樹脂製の保持器１４と、を備え、不図示のハウジングに外輪１１が内嵌されて使用される。また、転がり軸受１０は、オイル潤滑又はグリース潤滑で使用される。また、転がり軸受１０は、ハイブリッド・トランスミッション又は電気自動車に搭載されるモータの回転軸を支持する箇所に適用され、重荷重条件や、回転荷重又は軽荷重条件で使用されている。   As shown in FIG. 1, the rolling bearing 10 of the present embodiment includes an outer ring 11 having an outer ring raceway surface 11a on an inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12a on an outer peripheral surface, an outer ring raceway surface 11a and an inner ring raceway. A plurality of balls (rolling elements) 13 disposed so as to be able to roll between the surface 12a and a resin cage 14 that holds the plurality of balls 13 at equal intervals in the circumferential direction. An outer ring 11 is fitted into the illustrated housing for use. The rolling bearing 10 is used in oil lubrication or grease lubrication. The rolling bearing 10 is applied to a portion that supports a rotating shaft of a motor mounted on a hybrid transmission or an electric vehicle, and is used under heavy load conditions, rotational loads, or light load conditions.

また、外輪１１の外周面１１ｂに、２つの環状溝１５，１５が全周に亘って形成されると共に、この２つの環状溝１５，１５に、外輪１１の外周面１１ｂでのクリープの発生を防止するための断面略円形状の環状弾性体１６がそれぞれ装着されている。   In addition, two annular grooves 15 and 15 are formed on the outer peripheral surface 11b of the outer ring 11 over the entire circumference, and creep is generated on the outer peripheral surface 11b of the outer ring 11 in the two annular grooves 15 and 15. Each of the annular elastic bodies 16 having a substantially circular cross section for prevention is mounted.

また、２つの環状溝１５，１５は、軸受中心Ｏを通り軸受端面に平行な軸方向中心線ＣＬを中心にして対称位置に形成されている。また、環状弾性体１６としては、ゴムや樹脂などを材料としたＯリングなどを挙げることができる。なお、２つの環状溝１５，１５は、軸受１０の方向性を識別できるように、一方の溝形状を異ならせてもよい。   The two annular grooves 15 and 15 are formed at symmetrical positions around an axial center line CL passing through the bearing center O and parallel to the bearing end surface. Examples of the annular elastic body 16 include an O-ring made of rubber or resin. The two annular grooves 15 and 15 may have different groove shapes so that the directionality of the bearing 10 can be identified.

そして、本実施形態の転がり軸受１０は、外輪１１の径方向最小肉厚をｈ１［ｍｍ］、環状溝１５と外輪軌道面１１ａとの間の最小肉厚をｈ２［ｍｍ］、玉１３の直径をＤａ［ｍｍ］、軸受荷重（動等価荷重）をＰ［Ｎ］、基本動定格荷重をＣｒ［Ｎ］とした場合において、０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ１／Ｄａ≦０．８、且つ０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ２／Ｄａ≦０．８を満たすように設定されている。   In the rolling bearing 10 of the present embodiment, the minimum radial thickness of the outer ring 11 is h1 [mm], the minimum thickness between the annular groove 15 and the outer ring raceway surface 11a is h2 [mm], and the diameter of the ball 13 is. Is Da [mm], the bearing load (dynamic equivalent load) is P [N], and the basic dynamic load rating is Cr [N], 0.29 · (P / Cr) + 0.26 ≦ h1 / Da ≦ 0.8 and 0.29 · (P / Cr) + 0.26 ≦ h2 / Da ≦ 0.8.

なお、ｈ１／Ｄａ、ｈ２／Ｄａが０．２９・（Ｐ／Ｃｒ）＋０．２６より小さくなる場合、外輪１１の剛性不足により、波打ち変形してクリープが発生する可能性がある。また、ｈ１／Ｄａ、ｈ２／Ｄａが０．８より大きくなる場合、転がり軸受１０に転動体である玉１３を組み込みにくくなる。即ち、転がり軸受１０を自動組立装置で組み立てる場合、通常最後に外輪１１を弾性変形させた状態で玉１３を組み込むため、上記最小肉厚ｈ１、ｈ２が０．８・Ｄａより大きくなる場合には、外輪１１を弾性変形させるために必要な荷重が大きくなり、外輪１１や玉１３に損傷が生じやすくなり、自動組立装置で組み立てることができなくなる可能性がある。   When h1 / Da and h2 / Da are smaller than 0.29 · (P / Cr) +0.26, there is a possibility that creep will occur due to undulation deformation due to insufficient rigidity of the outer ring 11. Moreover, when h1 / Da and h2 / Da are larger than 0.8, it is difficult to incorporate the balls 13 as rolling elements into the rolling bearing 10. That is, when the rolling bearing 10 is assembled by an automatic assembling apparatus, the ball 13 is usually assembled with the outer ring 11 elastically deformed last, so that the minimum thicknesses h1 and h2 are larger than 0.8 · Da. The load necessary for elastically deforming the outer ring 11 becomes large, the outer ring 11 and the ball 13 are likely to be damaged, and there is a possibility that the automatic assembly apparatus cannot be assembled.

以上説明したように、本実施形態の転がり軸受１０によれば、外輪１１の径方向最小肉厚をｈ１、環状溝１５と外輪軌道面１１ａとの間の最小肉厚をｈ２、玉１３の直径をＤａ、軸受荷重をＰ、基本動定格荷重をＣｒとした場合において、０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ１／Ｄａ≦０．８、且つ０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ２／Ｄａ≦０．８を満たすように設定されるため、外輪１１の径方向最小肉厚ｈ１及び環状溝１５と外輪軌道面１１ａとの間の最小肉厚ｈ２を適正化して、外輪１１の外周面１１ｂの波打ち変形を抑制することができる。これにより、オイル潤滑又はグリース潤滑下で、重荷重条件や、回転荷重又は軽荷重条件下で軸受１０が使用されたとしても、外輪１１の外周面１１ｂでのクリープの発生を防止することができる。   As described above, according to the rolling bearing 10 of the present embodiment, the radial minimum wall thickness of the outer ring 11 is h1, the minimum wall thickness between the annular groove 15 and the outer ring raceway surface 11a is h2, and the diameter of the ball 13 is. Is Da, bearing load is P, and basic dynamic load rating is Cr, 0.29 · (P / Cr) + 0.26 ≦ h1 / Da ≦ 0.8 and 0.29 · (P / Cr) Since + 0.26 ≦ h2 / Da ≦ 0.8 is set, the minimum radial thickness h1 of the outer ring 11 and the minimum thickness h2 between the annular groove 15 and the outer ring raceway surface 11a are optimized. The wavy deformation of the outer peripheral surface 11b of the outer ring 11 can be suppressed. Thereby, even if the bearing 10 is used under heavy load conditions, rotational loads, or light load conditions under oil lubrication or grease lubrication, the occurrence of creep on the outer peripheral surface 11b of the outer ring 11 can be prevented. .

また、本実施形態の転がり軸受１０によれば、保持器１４が樹脂製であるため、軸受１０の方向性を識別することができ、また、軸受回転中の玉１３の面粗度の悪化や発熱を抑制することができるため、軸受１０の高速回転性能や耐久性も向上することができる。   Further, according to the rolling bearing 10 of the present embodiment, since the cage 14 is made of resin, the directionality of the bearing 10 can be identified, and the deterioration of the surface roughness of the balls 13 during rotation of the bearing Since heat generation can be suppressed, the high-speed rotation performance and durability of the bearing 10 can be improved.

（第２実施形態）
次に、図２を参照して、本発明に係る転がり軸受の第２実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一或いは同等符号を付してその説明を省略或いは簡略化する。 (Second Embodiment)
Next, a second embodiment of the rolling bearing according to the present invention will be described with reference to FIG. Note that the same or equivalent parts as those in the first embodiment are given the same or equivalent reference numerals in the drawings, and the description thereof is omitted or simplified.

本実施形態の転がり軸受１０は、図２に示すように、モータの回転軸などを支持することにより、内輪１２にラジアル荷重Ｆｒが負荷されると共に、内輪１２の軸方向一端部（図２の左側端部）にアキシアル荷重Ｆａが負荷された状態で使用される。具体的には、アキシアル荷重Ｆａ／ラジアル荷重Ｆｒが０．３以上で、０．２・Ｃｒ以上のアキシアル荷重を含む重荷重が負荷された状態で使用される。   As shown in FIG. 2, the rolling bearing 10 of the present embodiment supports a rotating shaft of a motor and the like so that a radial load Fr is applied to the inner ring 12, and one axial end portion of the inner ring 12 (see FIG. 2). The axial load Fa is applied to the left end). Specifically, the axial load Fa / radial load Fr is 0.3 or more and a heavy load including an axial load of 0.2 · Cr or more is used.

そして、内輪１２の軸方向一端部に負荷されたアキシアル荷重Ｆａは、内輪１２から玉１３を介して外輪１１の上記軸方向中心軸ＣＬよりも軸方向他端側（図２の右側）に伝達され（図２の矢印Ａ参照）、外輪１１の上記軸方向中心軸ＣＬよりも軸方向他端側でアキシアル荷重Ｆａを受けている。換言すると、外輪１１の上記軸方向中心軸ＣＬよりも軸方向一端側（図２の左側）では、アキシアル荷重Ｆａを受けていない。   Then, the axial load Fa applied to one axial end portion of the inner ring 12 is transmitted from the inner ring 12 to the other axial end side (right side in FIG. 2) of the outer ring 11 with respect to the axial center axis CL via the ball 13. 2 (see arrow A in FIG. 2), the axial load Fa is received at the other axial end side of the outer ring 11 with respect to the axial center axis CL. In other words, the axial load Fa is not received at one axial end side (left side in FIG. 2) of the outer ring 11 with respect to the axial center axis CL.

そして、本実施形態では、外輪１１の外周面１１ｂの上記軸方向中心線ＣＬよりもアキシアル荷重Ｆａを受けていない側、即ち、上記軸方向中心線ＣＬよりも軸方向一端側（図２の左側）に１つの環状溝１５が全周に亘って形成されると共に、この１つの環状溝１５に、外輪１１の外周面１１ｂでのクリープの発生を防止するための断面略円形状の環状弾性体１６が装着されている。   In the present embodiment, the side of the outer peripheral surface 11b of the outer ring 11 that is not receiving the axial load Fa from the axial center line CL, that is, the axial one end side from the axial center line CL (the left side in FIG. 2). ) Is formed over the entire circumference, and an annular elastic body having a substantially circular cross section for preventing the occurrence of creep on the outer peripheral surface 11b of the outer ring 11 in the one annular groove 15. 16 is attached.

以上説明したように、本実施形態の転がり軸受１０によれば、アキシアル荷重Ｆａ／ラジアル荷重Ｆｒが０．３以上で、０．２・Ｃｒ以上のアキシアル荷重を含む重荷重が負荷された状態において、外輪１１の外周面１１ｂの上記軸方向中心線ＣＬよりもアキシアル荷重Ｆａを受けていない側に環状溝１５が形成され、この環状溝１５に環状弾性体１６が装着されるため、外輪１１のアキシアル荷重Ｆａを受ける部分に環状溝が形成されず、外輪１１のアキシアル荷重Ｆａを受ける部分の剛性を確保することができる。これにより、外輪１１の外周面１１ｂの波打ち変形を更に抑制することができるので、オイル潤滑又はグリース潤滑下で、重荷重条件や、回転荷重又は軽荷重条件下で軸受１０が使用されたとしても、外輪１１の外周面１１ｂでのクリープの発生を更に防止することができる。
その他の構成及び作用効果については、上記第１実施形態と同様である。 As described above, according to the rolling bearing 10 of the present embodiment, the axial load Fa / radial load Fr is 0.3 or more and a heavy load including an axial load of 0.2 · Cr or more is applied. An annular groove 15 is formed on the outer circumferential surface 11b of the outer ring 11 on the side not receiving the axial load Fa from the axial center line CL, and the annular elastic body 16 is attached to the annular groove 15, so that the outer ring 11 An annular groove is not formed in the portion that receives the axial load Fa, and the rigidity of the portion that receives the axial load Fa of the outer ring 11 can be ensured. Thereby, since the wavy deformation of the outer peripheral surface 11b of the outer ring 11 can be further suppressed, even if the bearing 10 is used under heavy load conditions, rotational loads, or light load conditions under oil lubrication or grease lubrication. Further, the occurrence of creep on the outer peripheral surface 11b of the outer ring 11 can be further prevented.
About another structure and an effect, it is the same as that of the said 1st Embodiment.

なお、本発明は上記各実施形態に例示したものに限定されるものではなく、本発明の要旨を逸脱しない範囲において適宜変更可能である。
例えば、上記実施形態では、複数の環状溝を同じ形状としたが、これに限定されず、異なる形状であってもよく、また、形成位置が異なっていてもよい。
また、上記実施形態では、環状弾性体を断面略円形状としたが、これに限定されず、例えば、断面矩形状、断面多角形状のものなどであってもよい。
また、環状弾性体の材質としては、ゴムや樹脂の他、種々の材料を使用することができる。
また、外輪の外周面に固体潤滑皮膜が施されていてもよい。この場合、軸受の耐クリープ性能を更に高めることができる。
また、上記実施形態では、転動体を玉として例示したが、これに限定されず、円すいころ、円筒ころなど種々のものを採用することができる。 In addition, this invention is not limited to what was illustrated by said each embodiment, In the range which does not deviate from the summary of this invention, it can change suitably.
For example, in the above-described embodiment, the plurality of annular grooves have the same shape. However, the present invention is not limited to this, and different shapes may be used, and the formation positions may be different.
Moreover, in the said embodiment, although the cyclic | annular elastic body was made into cross-sectional substantially circular shape, it is not limited to this, For example, a cross-sectional rectangular shape, a cross-sectional polygonal shape, etc. may be sufficient.
Further, as the material of the annular elastic body, various materials can be used in addition to rubber and resin.
Further, a solid lubricant film may be applied to the outer peripheral surface of the outer ring. In this case, the creep resistance performance of the bearing can be further improved.
Moreover, in the said embodiment, although the rolling element was illustrated as a ball | bowl, it is not limited to this, Various things, such as a tapered roller and a cylindrical roller, are employable.

１０ 転がり軸受
１１ 外輪
１１ａ 外輪軌道面
１１ｂ 外周面
１２ 内輪
１２ａ 内輪軌道面
１３ 玉（転動体）
１４ 保持器
１５ 環状溝
１６ 環状弾性体
Ｏ 軸受中心
ＣＬ 軸方向中心線 DESCRIPTION OF SYMBOLS 10 Rolling bearing 11 Outer ring 11a Outer ring raceway surface 11b Outer peripheral surface 12 Inner ring 12a Inner ring raceway surface 13 Ball (rolling element)
14 Cage 15 Annular groove 16 Annular elastic body O Bearing center CL Axial direction center line

Claims (3)

内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、前記外輪軌道面と前記内輪軌道面との間に転動自在に配置される複数の転動体と、を備え、
前記外輪の外周面に、少なくとも１つの環状溝が全周に亘って形成され、
前記環状溝に、クリープの発生を防止するための環状弾性体が装着される転がり軸受であって、
前記外輪の径方向最小肉厚をｈ１、前記環状溝と前記外輪軌道面との間の最小肉厚をｈ２、前記転動体の直径をＤａ、軸受荷重をＰ、基本動定格荷重をＣｒとした場合において、
０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ１／Ｄａ≦０．８、且つ
０．２９・（Ｐ／Ｃｒ）＋０．２６≦ｈ２／Ｄａ≦０．８
を満たすように設定されることを特徴とする転がり軸受。 An outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rolling elements arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface, Prepared,
On the outer circumferential surface of the outer ring, at least one annular groove is formed over the entire circumference,
A rolling bearing in which an annular elastic body for preventing the occurrence of creep is attached to the annular groove,
The minimum radial thickness of the outer ring is h1, the minimum thickness between the annular groove and the outer ring raceway surface is h2, the diameter of the rolling element is Da, the bearing load is P, and the basic dynamic load rating is Cr. In case
0.29 · (P / Cr) + 0.26 ≦ h1 / Da ≦ 0.8 and 0.29 · (P / Cr) + 0.26 ≦ h2 / Da ≦ 0.8
A rolling bearing characterized by being set to satisfy 前記内輪にアキシアル荷重を含む重荷重が負荷され、前記内輪から前記転動体を介して前記外輪にアキシアル荷重が伝達される状態において、
前記環状溝は、軸受中心を通り軸受端面に平行な軸方向中心線よりもアキシアル荷重を受けていない側に形成されることを特徴とする請求項１に記載の転がり軸受。 In a state where a heavy load including an axial load is applied to the inner ring, and the axial load is transmitted from the inner ring to the outer ring via the rolling elements,
The rolling bearing according to claim 1, wherein the annular groove is formed on a side not passing an axial load from an axial center line passing through the bearing center and parallel to the bearing end surface. ハイブリッド・トランスミッション又は電気自動車に搭載されるモータの回転軸を支持するために使用され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 or 2, wherein the rolling bearing is used for supporting a rotating shaft of a motor mounted on a hybrid transmission or an electric vehicle.
JP2013109060A 2013-05-23 2013-05-23 Rolling bearing Active JP6064783B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2013109060A JP6064783B2 (en) 2013-05-23 2013-05-23 Rolling bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2013109060A JP6064783B2 (en) 2013-05-23 2013-05-23 Rolling bearing

Publications (2)

Publication Number Publication Date
JP2014228079A true JP2014228079A (en) 2014-12-08
JP6064783B2 JP6064783B2 (en) 2017-01-25

Family

ID=52128118

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2013109060A Active JP6064783B2 (en) 2013-05-23 2013-05-23 Rolling bearing

Country Status (1)

Country Link
JP (1) JP6064783B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018009669A (en) * 2016-07-15 2018-01-18 株式会社ジェイテクト Rolling bearing
CN109695628A (en) * 2017-10-20 2019-04-30 舍弗勒技术股份两合公司 Have slotted bearing race and bearing

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06280860A (en) * 1993-03-02 1994-10-07 Nippon Seiko Kk Ball bearing device
JP2004028285A (en) * 2002-06-28 2004-01-29 Nsk Ltd Pulley device with built-in one-way clutch
JP2004052966A (en) * 2002-07-23 2004-02-19 Nsk Ltd Roller bearing for belt type continuously variable transmission
JP2005048860A (en) * 2003-07-28 2005-02-24 Nsk Ltd Rolling bearing
JP2006329368A (en) * 2005-05-27 2006-12-07 Nsk Ltd Bearing for resin pulley
JP2011247660A (en) * 2010-05-25 2011-12-08 Mitsubishi Heavy Ind Ltd Life monitoring method of bearing
WO2012123710A1 (en) * 2011-03-16 2012-09-20 Flybrid Automotive Limited High speed flywheel
WO2013011704A1 (en) * 2011-07-15 2013-01-24 日本精工株式会社 Conical roller bearing for wheel

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06280860A (en) * 1993-03-02 1994-10-07 Nippon Seiko Kk Ball bearing device
JP2004028285A (en) * 2002-06-28 2004-01-29 Nsk Ltd Pulley device with built-in one-way clutch
JP2004052966A (en) * 2002-07-23 2004-02-19 Nsk Ltd Roller bearing for belt type continuously variable transmission
JP2005048860A (en) * 2003-07-28 2005-02-24 Nsk Ltd Rolling bearing
JP2006329368A (en) * 2005-05-27 2006-12-07 Nsk Ltd Bearing for resin pulley
JP2011247660A (en) * 2010-05-25 2011-12-08 Mitsubishi Heavy Ind Ltd Life monitoring method of bearing
WO2012123710A1 (en) * 2011-03-16 2012-09-20 Flybrid Automotive Limited High speed flywheel
WO2013011704A1 (en) * 2011-07-15 2013-01-24 日本精工株式会社 Conical roller bearing for wheel

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018009669A (en) * 2016-07-15 2018-01-18 株式会社ジェイテクト Rolling bearing
CN109695628A (en) * 2017-10-20 2019-04-30 舍弗勒技术股份两合公司 Have slotted bearing race and bearing

Also Published As

Publication number Publication date
JP6064783B2 (en) 2017-01-25

Similar Documents

Publication Publication Date Title
JP6047999B2 (en) Rotating support device
JP2007333022A (en) Deep groove ball bearing
EP2700834B1 (en) Rolling bearing with dynamic pressure generating grooves formed in a raceway of a bearing ring
JP6064783B2 (en) Rolling bearing
JP2005042894A (en) Double row rolling bearing device
JP2011094716A (en) Thrust roller bearing
JP2015200393A (en) Rolling bearing with seal ring
US10001171B2 (en) Rolling bearing
JP2009052588A (en) Rolling bearing
JP2014105809A (en) Retainer for rolling bearing
WO2018198556A1 (en) Tapered roller bearing
JP2014159846A (en) Roller bearing and fixation device
JP6024291B2 (en) Rolling bearing
JP5029430B2 (en) Thrust roller bearing device
WO2024127741A1 (en) Rolling bearing
JP2019060441A (en) Ball bearing with seal
JP6967831B2 (en) Bearing device for wheels
JP2007327609A (en) Divided type roller bearing
JP2024031207A (en) Shaft-integrated angular contact ball bearing
JP2009210091A (en) Automatic aligning roller bearing
JP6759544B2 (en) Thrust roller bearing
JP2024086328A (en) Rolling bearings
JP2006258203A (en) Rolling bearing
JP2015068354A (en) Rolling bearing
JP2014240672A (en) Bearing device

Legal Events

Date Code Title Description
RD02 Notification of acceptance of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7422

Effective date: 20150126

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20160222

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20161116

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20161122

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20161205

R150 Certificate of patent or registration of utility model

Ref document number: 6064783

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150