JP2007078137A - Tapered roller bearing, deep groove ball bearing, and hub unit for vehicle - Google Patents

Tapered roller bearing, deep groove ball bearing, and hub unit for vehicle Download PDF

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JP2007078137A
JP2007078137A JP2005269920A JP2005269920A JP2007078137A JP 2007078137 A JP2007078137 A JP 2007078137A JP 2005269920 A JP2005269920 A JP 2005269920A JP 2005269920 A JP2005269920 A JP 2005269920A JP 2007078137 A JP2007078137 A JP 2007078137A
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inner ring
outer ring
raceway surface
ring raceway
tapered roller
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Japanese (ja)
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Masahito Matsui
雅人 松井
Shinji Hirakata
伸治 平方
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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
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing capable of preventing the creep without increasing a number of components and capable of improving durability and assembling performance. <P>SOLUTION: This tapered roller bearing is provided with 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, and a plurality of tapered rollers 13 arranged between the outer ring raceway surface 11a and the inner ring raceway surface 12a so as to freely roll along the peripheral direction. The inner ring 12 is fixed to a shaft by interference fit or clearance fit, and the outer ring 11 is fixed to a housing by interference fit or clearance fit. A peripheral channel 14 non-contact with the shaft is formed on an inner ring raceway surface position (a) on the inner peripheral surface of the inner ring 12. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、自動車の車軸の回転支持部や各種機械装置の回転支持部等に組み込まれる円すいころ軸受及び深溝玉軸受、並びに円すいころ軸受が組み込まれる車両用ハブユニットに関する。   The present invention relates to a tapered roller bearing and a deep groove ball bearing incorporated in a rotation support portion of an axle of an automobile, a rotation support portion of various mechanical devices, and the like, and a vehicle hub unit in which the tapered roller bearing is incorporated.

図１８は、従来の円すいころ軸受の一例を示したものであり、円すいころ軸受２００は、ハウジングに内嵌される外輪２０１と、軸に外嵌される内輪２０２と、外輪２０１と内輪２０２との間に転動自在に配置される複数の円すいころ２０３とを備える。   FIG. 18 shows an example of a conventional tapered roller bearing. A tapered roller bearing 200 includes an outer ring 201 fitted in a housing, an inner ring 202 fitted on a shaft, an outer ring 201 and an inner ring 202. And a plurality of tapered rollers 203 arranged so as to be freely rotatable.

この円すいころ軸受２００を軸及びハウジングに組み込んで使用する際、負荷される荷重が大きい場合や、内輪２０２と軸との間、及び外輪２０１とハウジングとの間がすき間ばめであったり、締まりばめでしめしろが小さかったりする場合、荷重負荷時に外輪２０１の外周面や内輪２０２の内周面の形状が円周方向に波状に変形して、内輪２０２と軸との間或いは外輪２０１とハウジングとの間で相対すべりが起きる、いわゆるクリープが発生する。このようなクリープが発生すると、摩耗やがたつきが生じ、回転の安定性や静粛性が損なわれ、軸受寿命が低下するといった問題が生じる。   When the tapered roller bearing 200 is used by being incorporated in the shaft and the housing, if the load to be applied is large, the gap between the inner ring 202 and the shaft, and the gap between the outer ring 201 and the housing is a clearance fit or tightening. When the interference is small, the outer peripheral surface of the outer ring 201 and the inner peripheral surface of the inner ring 202 are deformed into a wave shape in the circumferential direction when a load is applied, and the inner ring 202 and the shaft or the outer ring 201 and the housing So-called creep occurs, in which relative slip occurs between the two. When such creep occurs, wear and rattling occur, and the stability and quietness of rotation are impaired, resulting in a problem that the bearing life is reduced.

これらの問題を解決するために、キーを使用する方法や、すきまを減らしたり、しめしろを大きくすることで、クリープを防止する技術が種々提案されている（例えば、特許文献１〜４参照。）。特許文献１に記載の方法は、外輪とハウジングとの間に偏心したキー溝を設け、キー溝内に楔状のキーを挿入してクリープを防止している。   In order to solve these problems, various techniques for preventing creep by using a key, reducing the clearance, or increasing the interference are proposed (see, for example, Patent Documents 1 to 4). ). In the method described in Patent Document 1, an eccentric key groove is provided between the outer ring and the housing, and a wedge-shaped key is inserted into the key groove to prevent creep.

また、特許文献２に記載の深溝玉軸受は、内輪と軸との間に介装した間座を固定リングで軸方向に加圧して、間座を径方向に膨張させることで、内輪と軸とのクリープを防止している。   Further, the deep groove ball bearing described in Patent Document 2 pressurizes a spacer interposed between the inner ring and the shaft in the axial direction with a fixing ring, and expands the spacer in the radial direction, so that the inner ring and the shaft And creep.

さらに、特許文献３に記載の深溝玉軸受は、外輪の外周面を中凹形状に形成とし、外輪を外周面がハウジングと全面で接触するように変形させて、クリープを防止している。また、特許文献４に記載の深溝玉軸受は、クリープ発生を防止するために使用温度領域でのしめしろを確保しつつ、外輪の外周面に矩形状の周溝を形成することで、温度変化に伴う嵌め合い面におけるしめしろの変動、特に、低温時におけるしめしろの増加を許容している。
実開平１−８５５２７号公報 特開平７−２７９９８２号公報 特開平１０−３７９６７号公報 特開２００４−１１８０１号公報 Further, in the deep groove ball bearing described in Patent Document 3, the outer peripheral surface of the outer ring is formed in a concave shape, and the outer ring is deformed so that the outer peripheral surface is in contact with the entire surface of the housing to prevent creep. In addition, the deep groove ball bearing described in Patent Document 4 has a rectangular shape on the outer peripheral surface of the outer ring while ensuring interference in the operating temperature range in order to prevent the occurrence of creep. The interference of the interference on the mating surface accompanying the increase of the interference, particularly the increase of the interference at a low temperature is allowed.
Japanese Utility Model Publication No. 1-85527 JP-A-7-279982 Japanese Patent Laid-Open No. 10-37967 JP 2004-11801 A

しかしながら、特許文献１のように、ハウジングに偏心したキー溝を設け、キー溝内に楔状のキーを挿入してクリープを防止する場合、キーの強度低下による破損のおそれがあり、また、部品点数が増えてコストアップにつながるという問題がある。   However, as in Patent Document 1, when an eccentric key groove is provided in the housing and a wedge-shaped key is inserted into the key groove to prevent creep, there is a risk of damage due to a decrease in the strength of the key. There is a problem that increases the cost and leads to cost increase.

また、特許文献２の場合、内輪の軌道面に発生する円周方向応力が過大になり、耐久性が損なわれたり、組立性を悪化させるという問題がある。   Further, in the case of Patent Document 2, there is a problem that the circumferential stress generated on the raceway surface of the inner ring becomes excessive, and the durability is impaired or the assemblability is deteriorated.

さらに、クリープは、荷重負荷を受けた外輪及び内輪が軌道面位置で波形に変形し、外輪とハウジング及び内輪と軸との嵌め合い部で、すべりが発生することにより生じる。このため、特許文献３のように、外輪の外周面全面がハウジングと接触している場合、荷重負荷による軌道面位置での変形が嵌め合いに影響を及ぼし、クリープを発生する虞がある。   Further, creep occurs when the outer ring and the inner ring that have received a load are deformed into a wave shape at the raceway surface position, and slip occurs at the fitting portion between the outer ring and the housing, and the inner ring and the shaft. For this reason, as in Patent Document 3, when the entire outer peripheral surface of the outer ring is in contact with the housing, deformation at the raceway surface position due to a load load affects the fit, and creep may occur.

また、特許文献４に記載の深溝玉軸受では、温度変化に伴うしめしろの変動を許容しつつ、クリープの発生を防止することができるが、荷重の負荷によるクリープの発生について考慮されておらず、また、軸受剛性の向上を図ることがさらに求められる。   Further, in the deep groove ball bearing described in Patent Document 4, it is possible to prevent the occurrence of creep while allowing fluctuations in the interference due to the temperature change, but the generation of creep due to the load is not considered. Further, it is further required to improve the bearing rigidity.

本発明は、このような不都合を解消するためになされたものであり、その目的は、部品点数を増やすことなく、クリープを防止することができるとともに、耐久性及び組立性の向上を図ることができる円すいころ軸受及び深溝玉軸受、並びに車両用ハブユニットを提供することにある。   The present invention has been made to eliminate such inconveniences, and its purpose is to prevent creep without increasing the number of parts and to improve durability and assemblability. It is an object of the present invention to provide a tapered roller bearing and a deep groove ball bearing, and a vehicle hub unit.

本発明の上記目的は、以下の構成によって達成される。
（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周方向に転動自在に配置される複数の円すいころとを備え、内輪が締まりばめ又はすき間ばめにより軸に固定され、外輪が締まりばめ又はすき間ばめによりハウジングに固定された状態で使用される円すいころ軸受であって、
内輪の内周面の内輪軌道面位置と外輪の外周面の外輪軌道面位置のいずれか一方の軌道面位置には、軌道面位置と対向する軸又はハウジングと非接触な周方向溝が形成されることを特徴とする円すいころ軸受。
（２） 外輪と内輪は、一対の外輪軌道面と一対の内輪軌道面をそれぞれ備え、
円すいころは一対の外輪軌道面と一対の内輪軌道面間に配置される複列の円すいころであって、
外輪又は内輪は、一対の外輪軌道面又は一対の内輪軌道面を単一の部材によって形成し、
周方向溝は、内輪の内周面の一対の内輪軌道面位置、及び外輪の外周面の一対の外輪軌道面位置の少なくとも一つの軌道面位置に形成されることを特徴とする（１）に記載の円すいころ軸受。
（３） （１）又は（２）に記載の円すいころ軸受を組み込んだことを特徴とする車両用ハブユニット。
（４） 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周方向に転動自在に配置される複数の玉とを備え、内輪が締まりばめ又はすき間ばめにより軸に固定され、外輪が締まりばめ又はすき間ばめによりハウジングに固定された状態で使用される深溝玉軸受であって、
内輪の内周面の内輪軌道面位置と外輪の外周面の外輪軌道面位置のいずれか一方の軌道面位置には、軌道面位置と対向する軸又はハウジングと非接触である、円弧断面、短辺側両隅部が湾曲形状の台形断面、頂点が湾曲形状の三角形断面のいずれかの周方向溝が形成されることを特徴とする深溝玉軸受。
（５） 周方向溝の最大深さが５〜２０μｍであることを特徴とする（４）に記載の深溝玉軸受。
なお、本発明の軌道面位置である、内輪軌道面位置は内輪軌道面と軸方向において重なる内輪の内周面を表し、外輪軌道面位置は外輪軌道面と軸方向において重なる外輪の外周面を表す。 The above object of the present invention is achieved by the following configurations.
(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 cones arranged between the outer ring raceway surface and the inner ring raceway surface so as to be freely rollable in the circumferential direction. A tapered roller bearing used in a state in which an inner ring is fixed to a shaft by an interference fit or a clearance fit, and an outer ring is fixed to a housing by an interference fit or a clearance fit,
Either one of the inner ring raceway surface position on the inner ring inner surface and the outer ring raceway position on the outer ring outer ring surface is formed with a circumferential groove that is not in contact with the shaft or housing that faces the track surface position. Tapered roller bearings characterized by that.
(2) The outer ring and the inner ring each have a pair of outer ring raceway surfaces and a pair of inner ring raceway surfaces,
A tapered roller is a double row tapered roller disposed between a pair of outer ring raceway surfaces and a pair of inner ring raceway surfaces,
The outer ring or inner ring is formed of a single member with a pair of outer ring raceway surfaces or a pair of inner ring raceway surfaces,
The circumferential groove is formed in at least one raceway surface position of a pair of inner ring raceway surface positions on the inner circumference surface of the inner ring and a pair of outer ring raceway surface positions on the outer circumference surface of the outer ring. The tapered roller bearing described.
(3) A vehicle hub unit comprising the tapered roller bearing according to (1) or (2).
(4) An outer ring having an outer ring raceway surface on the inner peripheral surface, an inner ring having an inner ring raceway surface on the outer peripheral surface, and a plurality of balls arranged so as to be able to roll in the circumferential direction between the outer ring raceway surface and the inner ring raceway surface. A deep groove ball bearing used in a state where the inner ring is fixed to the shaft by interference fit or clearance fit and the outer ring is fixed to the housing by interference fit or clearance fit,
Either the inner ring raceway surface position on the inner ring inner surface or the outer ring raceway position on the outer ring outer ring surface has a circular cross section, short contact with the shaft or housing facing the track surface position. A deep groove ball bearing characterized in that a circumferential groove having either a trapezoidal cross section with a curved shape at both side corners or a triangular cross section with a curved shape at a vertex is formed.
(5) The deep groove ball bearing according to (4), wherein the circumferential groove has a maximum depth of 5 to 20 μm.
The inner raceway surface position, which is the raceway surface position of the present invention, represents the inner peripheral surface of the inner ring that overlaps the inner ring raceway surface in the axial direction, and the outer ring raceway surface position represents the outer peripheral surface of the outer ring that overlaps the outer ring raceway surface in the axial direction. To express.

本発明の円すいころ軸受及び車両用ハブユニットによれば、内輪の内周面の内輪軌道面位置と外輪の外周面の外輪軌道面位置のいずれか一方の軌道面位置に、この軌道面位置と対向する軸又はハウジングと非接触な周方向溝が形成されるので、荷重負荷によって、外輪の外周面や内輪の内周面の形状が円周方向に波状に変形した際に、該変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、クリープの発生を防止することができる。また、しめしろを大きくする必要がないので、外輪又は内輪の軌道面に発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   According to the tapered roller bearing and the vehicle hub unit of the present invention, the raceway surface position is set to one of the raceway surface position of the inner ring raceway surface of the inner ring and the outer ring raceway position of the outer race of the outer ring. Since a circumferential groove that is not in contact with the opposing shaft or housing is formed, the deformation is fitted when the shape of the outer peripheral surface of the outer ring or the inner peripheral surface of the inner ring is deformed in the circumferential direction by a load. The influence on the interface can be suppressed, and the occurrence of creep can be prevented without increasing the number of parts. In addition, since it is not necessary to increase the interference, it is possible to avoid excessive circumferential stress generated on the raceway surface of the outer ring or the inner ring, thereby improving durability and assemblability. Can do.

また、本発明の深溝玉軸受によれば、内輪の内周面の内輪軌道面位置と外輪の外周面の外輪軌道面位置のいずれか一方の軌道面位置に、この軌道面位置と対向する軸又はハウジングと非接触である、円弧断面、短辺側両隅部が湾曲形状の台形断面、頂点が湾曲形状の三角形断面のいずれかの周方向溝が形成されるので、荷重負荷によって、外輪の外周面や内輪の内周面の形状が円周方向に波状に変形した際に、該変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、クリープの発生を防止することができる。また、しめしろを大きくする必要がないので、外輪又は内輪の軌道面に発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。更に、周方向溝の形状が、円弧断面、短辺側両隅部が湾曲形状の台形断面、頂点が湾曲形状の三角形断面のいずれかであるので、矩形断面の周方向溝に比べて、軸受の剛性低下を抑制することができる。   Further, according to the deep groove ball bearing of the present invention, the shaft facing the raceway surface position at one of the inner raceway surface position of the inner race surface of the inner ring and the outer raceway surface position of the outer race surface of the outer ring. Alternatively, a circumferential groove with either a circular cross section, a trapezoidal cross section with curved corners at both corners on the short side, or a triangular cross section with a curved shape at the apex, which is not in contact with the housing, is formed. When the shape of the outer peripheral surface or the inner peripheral surface of the inner ring deforms in a wave shape in the circumferential direction, the influence of the deformation on the mating surface can be suppressed, preventing the occurrence of creep without increasing the number of parts. can do. Further, since it is not necessary to increase the interference, it is possible to avoid excessive circumferential stress generated on the raceway surface of the outer ring or the inner ring, thereby improving durability and assemblability. Can do. Furthermore, the shape of the circumferential groove is either an arc cross-section, a trapezoidal cross-section with curved corners at both corners on the short side, or a triangular cross-section with a curved apex. Can be suppressed.

以下、本発明の各実施形態について図面を参照して詳細に説明する。   Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

（第１実施形態）
本発明の第１実施形態である円すいころ軸受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との間に周方向に転動自在に配置される複数の円すいころ１３とを備える。円すいころ軸受１０は、外輪１１が、締まりばめ又はすき間ばめによりハウジング（図示せず）に固定され、内輪１２が、締まりばめ又はすき間ばめにより軸（図示せず）に固定された状態で使用される。 (First embodiment)
As shown in FIG. 1, a tapered roller bearing 10 according to the first embodiment of the present invention 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, and an outer ring. A plurality of tapered rollers 13 are provided between the raceway surface 11a and the inner ring raceway surface 12a so as to be freely rollable in the circumferential direction. In the tapered roller bearing 10, an outer ring 11 is fixed to a housing (not shown) by interference fit or clearance fit, and an inner ring 12 is fixed to a shaft (not shown) by interference fit or clearance fit. Used in state.

軸方向において内輪軌道面１２ａと重なる内輪１２の内周面の内輪軌道面位置ａには、略矩形断面の周方向溝１４が周方向全周に亘って設けられている。この周方向溝１４は、内輪１２が軸に固定された状態において、軸と非接触に維持される。また、周方向溝１４は、内輪軌道面位置ａ内に形成されればよく、内輪軌道面１２ａの軸方向寸法以下であればよい。   A circumferential groove 14 having a substantially rectangular cross section is provided over the entire circumference in the inner ring raceway surface position a on the inner circumferential surface of the inner ring 12 that overlaps the inner ring raceway surface 12a in the axial direction. The circumferential groove 14 is maintained in non-contact with the shaft when the inner ring 12 is fixed to the shaft. Further, the circumferential groove 14 only needs to be formed in the inner ring raceway surface position a, and may be smaller than the axial dimension of the inner ring raceway surface 12a.

このように、本実施形態では、円すいころ軸受１０の内輪１２の内周面の内輪軌道面位置ａに、軸と非接触な周方向溝１４が形成されるので、荷重負荷によって、内輪１２の内周面の形状が円周方向に波状に変形した際に、この変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、内輪１２と軸との間のクリープの発生を防止することができる。   Thus, in this embodiment, since the circumferential groove 14 that is not in contact with the shaft is formed in the inner ring raceway surface position a on the inner circumferential surface of the inner ring 12 of the tapered roller bearing 10, the load on the inner ring 12 is increased. When the shape of the inner peripheral surface is deformed in a wave shape in the circumferential direction, the influence of this deformation on the fitting surface can be suppressed, and the creep between the inner ring 12 and the shaft can be reduced without increasing the number of parts. Occurrence can be prevented.

また、内輪１２と軸とのしめしろを大きくする必要がないので、内輪１２の内輪軌道面１２ａに発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   Further, since there is no need to increase the interference between the inner ring 12 and the shaft, it is possible to avoid excessive circumferential stress generated on the inner ring raceway surface 12a of the inner ring 12, thereby improving durability and durability. Assemblability can be improved.

（第２実施形態）
本発明の第２実施形態である複列円すいころ軸受２０は、図２に示すように、内周面に一対の外輪軌道面２１ａを有する単一の部材である外輪２１と、外周面に内輪軌道面２２ａをそれぞれ有する一対の内輪２２と、一対の内輪２２間に介装された内輪間座２５と、一対の外輪軌道面２１ａと一対の内輪軌道面２２ａとの間に周方向に転動自在に配置される複列の円すいころ２３とを備える。複列円すいころ軸受２０は、外輪２１が、締まりばめ又はすき間ばめによりハウジング（図示せず）に固定され、一対の内輪２２が、締まりばめ又はすき間ばめにより軸（図示せず）に固定された状態で使用される。 (Second Embodiment)
As shown in FIG. 2, the double-row tapered roller bearing 20 according to the second embodiment of the present invention includes an outer ring 21 that is a single member having a pair of outer ring raceway surfaces 21a on the inner peripheral surface, and an inner ring on the outer peripheral surface. Roll in the circumferential direction between a pair of inner rings 22 each having a raceway surface 22a, an inner ring spacer 25 interposed between the pair of inner rings 22, and a pair of outer ring raceway surfaces 21a and a pair of inner ring raceway surfaces 22a. A double row tapered roller 23 is provided. In the double row tapered roller bearing 20, an outer ring 21 is fixed to a housing (not shown) by an interference fit or a clearance fit, and a pair of inner rings 22 are shafts (not shown) by an interference fit or a clearance fit. Used in a fixed state.

軸方向において内輪軌道面２２ａと重なる一対の内輪２２の各内周面の内輪軌道面位置ａには、略矩形断面の周方向溝２４が周方向全周に沿って設けられている。この周方向溝２４は、各内輪２２が軸に固定された状態において、軸と非接触に維持される。また、各周方向溝２４は、内輪軌道面位置ａ内に形成されればよく、内輪軌道面２２ａの軸方向寸法以下であればよい。なお、周方向溝２４は、一対の内輪２２の内輪軌道面位置ａにそれぞれ形成されているが、一方のみに形成されてもよい。この場合、負荷の大きくかかる側の内輪２２の内輪軌道面位置ａに周方向溝２４を形成するのが好ましい。また、一対の内輪２２間に介装される内輪間座２５は任意に設けられ、内輪間座を必ずしも設ける必要はない。   A circumferential groove 24 having a substantially rectangular cross section is provided along the entire circumference in the inner ring raceway surface position a of each inner circumferential surface of the pair of inner rings 22 overlapping the inner ring raceway surface 22a in the axial direction. The circumferential groove 24 is maintained in non-contact with the shaft in a state where each inner ring 22 is fixed to the shaft. Each circumferential groove 24 only needs to be formed in the inner ring raceway surface position a, and may be smaller than or equal to the axial dimension of the inner ring raceway surface 22a. In addition, although the circumferential groove | channel 24 is each formed in the inner ring raceway surface position a of a pair of inner ring | wheel 22, you may form in only one side. In this case, it is preferable to form the circumferential groove 24 in the inner ring raceway surface position a of the inner ring 22 on the side where a large load is applied. Further, the inner ring spacer 25 interposed between the pair of inner rings 22 is arbitrarily provided, and the inner ring spacer is not necessarily provided.

このように、本実施形態では、複列円すいころ軸受２０の内輪２２の内周面の内輪軌道面位置ａに、軸と非接触な周方向溝２４が形成されるので、荷重負荷によって、内輪２２の内周面の形状が円周方向に波状に変形した際に、この変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、内輪２２と軸との間のクリープの発生を防止することができる。   Thus, in this embodiment, since the circumferential groove 24 that is not in contact with the shaft is formed at the inner ring raceway surface position a on the inner circumferential surface of the inner ring 22 of the double row tapered roller bearing 20, the inner ring is caused by a load load. When the shape of the inner peripheral surface of 22 is deformed in a wave shape in the circumferential direction, it is possible to suppress the influence of this deformation on the fitting surface, and without increasing the number of parts, between the inner ring 22 and the shaft. Creep can be prevented from occurring.

また、内輪２２と軸とのしめしろを大きくする必要がないので、内輪２２の内輪軌道面２２ａに発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   Further, since there is no need to increase the interference between the inner ring 22 and the shaft, it is possible to avoid excessive circumferential stress generated on the inner ring raceway surface 22a of the inner ring 22, thereby improving durability and durability. Assemblability can be improved.

（第３実施形態）
本発明の第３実施形態である車両用ハブユニット３０は、図３に示すように、ハウジングとしてのナックル３６と軸としてのハブ３７との間に、第１実施形態の円すいころ軸受１０を２個組み込んだものである。外輪１１は、締まりばめ又はすき間ばめによりナックル３６に嵌め込まれ、内輪１２は、締まりばめ又はすき間ばめによりハブ３７に嵌め込まれる。また、各内輪１２間には内輪間座３５が介装されている。
その他の構成及び作用効果については、第１実施形態と同様である。なお、本実施形態は、内輪回転タイプを例示しているが、外輪回転タイプに適用してもよい。 (Third embodiment)
As shown in FIG. 3, the vehicle hub unit 30 according to the third embodiment of the present invention includes two tapered roller bearings 10 according to the first embodiment between a knuckle 36 as a housing and a hub 37 as a shaft. It is one that has been incorporated. The outer ring 11 is fitted into the knuckle 36 by an interference fit or clearance fit, and the inner ring 12 is fitted into the hub 37 by an interference fit or clearance fit. An inner ring spacer 35 is interposed between the inner rings 12.
About another structure and an effect, it is the same as that of 1st Embodiment. In addition, although this embodiment has illustrated the inner ring | wheel rotation type, you may apply to an outer ring | wheel rotation type.

（第４実施形態）
本発明の第４実施形態である車両用ハブユニット４０は、図４に示すように、ハウジングとしてのナックル４６と軸としてのハブ４７との間に、複列円すいころ軸受４８を組み込んだものであり、所謂、第１世代のハブユニットに適用された例である。複列円すいころ軸受４８は、内周面に一対の外輪軌道面４１ａを有する単一の部材である外輪４１と、外周面に内輪軌道面４２ａを有する一対の内輪４２と、一対の外輪軌道面４１ａと一対の内輪軌道面４２ａとの間に周方向に転動自在に配置される複列の円すいころ４３とを備える。複列円すいころ軸受４８は、外輪４１が、締まりばめ又はすき間ばめによりナックル４６に固定され、一対の内輪４２が締まりばめ又はすき間ばめによりハブ４７に固定された状態で用いられる。 (Fourth embodiment)
As shown in FIG. 4, a vehicle hub unit 40 according to a fourth embodiment of the present invention incorporates a double row tapered roller bearing 48 between a knuckle 46 as a housing and a hub 47 as a shaft. This is an example applied to a so-called first generation hub unit. The double row tapered roller bearing 48 includes an outer ring 41 that is a single member having a pair of outer ring raceway surfaces 41a on an inner peripheral surface, a pair of inner rings 42 having an inner ring raceway surface 42a on an outer peripheral surface, and a pair of outer ring raceway surfaces. A double row tapered roller 43 is provided between 41a and the pair of inner ring raceway surfaces 42a so as to be freely rollable in the circumferential direction. The double-row tapered roller bearing 48 is used in a state where the outer ring 41 is fixed to the knuckle 46 by interference fit or clearance fit, and the pair of inner rings 42 is fixed to the hub 47 by interference fit or clearance fit.

そして、軸方向において内輪軌道面４２ａに重なる一対の内輪４２の各内周面の内輪軌道面位置ａには、略矩形断面の周方向溝４４が周方向全周に亘って設けられている。この周方向溝４４は、内輪４２がハブ４７に固定された状態において、ハブ４７と非接触に維持される。また、各周方向溝４４は、内輪軌道面位置ａ内に形成されればよく、内輪軌道面２２ａの軸方向寸法以下であればよい。また、周方向溝４４は、一対の内輪４２の内輪軌道面位置ａにそれぞれ形成されているが、一方のみに形成されてもよい。この場合、負荷の大きくかかる側の内輪４２の内輪軌道面位置ａに周方向溝４４を形成するのが好ましい。更に、本実施形態は、内輪回転タイプを例示しているが、外輪回転タイプに適用してもよい。
その他の構成及び作用については、第２実施形態のものと同様である。 A circumferential groove 44 having a substantially rectangular cross section is provided over the entire circumference in the inner ring raceway surface position a of each inner circumferential surface of the pair of inner rings 42 overlapping the inner ring raceway surface 42a in the axial direction. The circumferential groove 44 is kept out of contact with the hub 47 when the inner ring 42 is fixed to the hub 47. Each circumferential groove 44 may be formed in the inner ring raceway surface position a, and may be smaller than the axial dimension of the inner ring raceway surface 22a. Moreover, although the circumferential groove | channel 44 is each formed in the inner ring raceway surface position a of a pair of inner ring 42, you may form in only one side. In this case, it is preferable to form the circumferential groove 44 in the inner ring raceway surface position a of the inner ring 42 on the side where a large load is applied. Furthermore, although this embodiment has illustrated the inner ring | wheel rotation type, you may apply to an outer ring | wheel rotation type.
Other configurations and operations are the same as those of the second embodiment.

（第５実施形態）
本発明の第５実施形態である車両用ハブユニット５０は、図５に示すように、第４実施形態（図４）の複列円すいころ軸受４８の外輪４１にフランジ５１を設けたものであり、第２世代のハブユニットに適用された例である。本実施形態は、フランジ５１が車体に固定されて、内輪回転で用いられる。 (Fifth embodiment)
As shown in FIG. 5, the vehicle hub unit 50 according to the fifth embodiment of the present invention is provided with a flange 51 on the outer ring 41 of the double row tapered roller bearing 48 of the fourth embodiment (FIG. 4). This is an example applied to the second generation hub unit. In the present embodiment, the flange 51 is fixed to the vehicle body and is used for inner ring rotation.

その他の構成及び作用については、上記第４実施形態と同様である。本実施形態についても、一対の内輪４２にそれぞれ周方向溝４４を設けているが、図６に示すように、一方の内輪４２のみに設けてもよい。この場合、特に、負荷の大きくかかる側の内輪４２に周方向溝４４を設けるのが好ましい。更に、本実施形態は、内輪回転タイプを例示しているが、フランジ５１を車軸に固定する外輪回転タイプに適用してもよい。   Other configurations and operations are the same as those in the fourth embodiment. Also in this embodiment, the circumferential grooves 44 are provided in the pair of inner rings 42, respectively, but may be provided only in one inner ring 42 as shown in FIG. In this case, it is particularly preferable to provide the circumferential groove 44 in the inner ring 42 on the side where the load is large. Furthermore, although this embodiment has illustrated the inner ring | wheel rotation type, you may apply to the outer ring | wheel rotation type which fixes the flange 51 to an axle.

（第６実施形態）
本発明の第６実施形態である円すいころ軸受６０は、図７に示すように、内周面に外輪軌道面６１ａを有する外輪６１と、外周面に内輪軌道面６２ａを有する内輪６２と、外輪軌道面６１ａと内輪軌道面６２ａとの間に周方向に転動自在に配置される複数の円すいころ６３とを備える。円すいころ軸受６０は、外輪６１が、締まりばめ又はすき間ばめによりハウジング（図示せず）に固定され、内輪６２が、締まりばめ又はすき間ばめにより軸（図示せず）に固定された状態で使用される。 (Sixth embodiment)
As shown in FIG. 7, the tapered roller bearing 60 according to the sixth embodiment of the present invention includes an outer ring 61 having an outer ring raceway surface 61a on an inner peripheral surface, an inner ring 62 having an inner ring raceway surface 62a on an outer peripheral surface, and an outer ring. A plurality of tapered rollers 63 are provided between the raceway surface 61a and the inner ring raceway surface 62a so as to be freely rollable in the circumferential direction. In the tapered roller bearing 60, an outer ring 61 is fixed to a housing (not shown) by an interference fit or clearance fit, and an inner ring 62 is fixed to a shaft (not shown) by an interference fit or clearance fit. Used in state.

軸方向において外輪軌道面６１ａと重なる外輪６１の外周面の外輪軌道面位置ｂには、略矩形断面の周方向溝６４が周方向全周に亘って設けられている。この周方向溝６４は、外輪６１がハウジングに固定された状態において、ハウジングと非接触に維持される。また、周方向溝６４は、外輪軌道面位置ｂ内に形成されればよく、外輪軌道面６１ａの軸方向寸法以下であればよい。   A circumferential groove 64 having a substantially rectangular cross section is provided over the entire circumference in the outer ring raceway surface position b on the outer circumferential surface of the outer ring 61 that overlaps the outer ring raceway surface 61a in the axial direction. The circumferential groove 64 is kept out of contact with the housing when the outer ring 61 is fixed to the housing. Moreover, the circumferential groove | channel 64 should just be formed in the outer ring raceway surface position b, and should just be below the axial direction dimension of the outer ring raceway surface 61a.

このように、本実施形態では、円すいころ軸受６０の外輪６１の外周面の外輪軌道面位置ｂに、ハウジングと非接触な周方向溝６４が形成されるので、荷重負荷によって、外輪６１の外周面の形状が円周方向に波状に変形した際に、この変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、外輪６１とハウジングとの間のクリープの発生を防止することができる。   As described above, in this embodiment, the circumferential groove 64 that is not in contact with the housing is formed at the outer ring raceway surface position b on the outer circumferential surface of the outer ring 61 of the tapered roller bearing 60. When the shape of the surface is deformed into a wave shape in the circumferential direction, the effect of this deformation on the mating surface can be suppressed, and the occurrence of creep between the outer ring 61 and the housing can be suppressed without increasing the number of parts. Can be prevented.

また、外輪６１とハウジングとのしめしろを大きくする必要がないので、外輪６１の外輪軌道面６１ａに発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   In addition, since it is not necessary to increase the interference between the outer ring 61 and the housing, it is possible to avoid excessive circumferential stress generated on the outer ring raceway surface 61a of the outer ring 61, thereby improving durability and durability. Assemblability can be improved.

（第７実施形態）
本発明の第７実施形態である複列円すいころ軸受７０は、図８に示すように、内周面に一対の外輪軌道面７１ａを有する単一の部材である外輪７１と、外周面に内輪軌道面７２ａを有する一対の内輪７２と、一対の内輪７２間に介装された内輪間座７５と、複列の外輪軌道面７１ａと一対の内輪軌道面７２ａとの間に周方向に転動自在に配置される複列の円すいころ７３とを備える。複列円すいころ軸受７０は、外輪７１が、締まりばめ又はすき間ばめによりハウジング（図示せず）に固定され、一対の内輪７２が締まりばめ又はすき間ばめにより軸（図示せず）に固定された状態で使用される。 (Seventh embodiment)
As shown in FIG. 8, the double-row tapered roller bearing 70 according to the seventh embodiment of the present invention includes an outer ring 71 that is a single member having a pair of outer ring raceway surfaces 71a on the inner peripheral surface, and an inner ring on the outer peripheral surface. Roll in the circumferential direction between a pair of inner rings 72 having a raceway surface 72a, an inner ring spacer 75 interposed between the pair of inner rings 72, a double row outer ring raceway surface 71a and a pair of inner ring raceway surfaces 72a. A double-row tapered roller 73 is provided. In the double row tapered roller bearing 70, an outer ring 71 is fixed to a housing (not shown) by an interference fit or a clearance fit, and a pair of inner rings 72 is fixed to a shaft (not shown) by an interference fit or a clearance fit. Used in a fixed state.

軸方向において外輪軌道面７１ａと重なる外輪７１の外周面の一対の外輪軌道面位置ｂには、列ごとに略矩形断面の周方向溝７４が周方向全周に沿って設けられている。この周方向溝７４は、外輪７１がハウジングに固定された状態において、ハウジングと非接触に維持される。また、各周方向溝７４は、外輪軌道面位置ｂ内に形成されればよく、外輪軌道面７１ａの軸方向寸法以下であればよい。なお、周方向溝７４は、一対の外輪軌道面位置ｂにそれぞれ形成されているが、一方のみに形成されてもよい。この場合、負荷の大きくかかる側の外輪軌道面位置ｂに周方向溝７４を形成するのが好ましい。また、一対の内輪７２間に介装される内輪間座７５は任意に設けられ、内輪間座を必ずしも設ける必要はない。   In a pair of outer ring raceway surface positions b on the outer peripheral surface of the outer ring 71 that overlaps the outer ring raceway surface 71a in the axial direction, circumferential grooves 74 having a substantially rectangular cross section are provided along the entire circumference in each row. The circumferential groove 74 is kept out of contact with the housing when the outer ring 71 is fixed to the housing. Each circumferential groove 74 may be formed in the outer ring raceway surface position b and may be equal to or smaller than the axial dimension of the outer ring raceway surface 71a. In addition, although the circumferential groove | channel 74 is each formed in a pair of outer ring raceway surface position b, you may form in only one side. In this case, it is preferable to form the circumferential groove 74 at the outer ring raceway surface position b on the side where a large load is applied. Further, the inner ring spacer 75 interposed between the pair of inner rings 72 is arbitrarily provided, and the inner ring spacer is not necessarily provided.

このように、本実施形態では、複列円すいころ軸受７０の外輪７１の外周面の外輪軌道面位置ｂに、ハウジングと非接触な周方向溝７４が形成されるので、荷重負荷によって、外輪７１の外周面の形状が円周方向に波状に変形した際に、この変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、外輪７１とハウジングとの間のクリープの発生を防止することができる。   Thus, in this embodiment, since the circumferential groove 74 that is not in contact with the housing is formed at the outer ring raceway surface position b on the outer circumferential surface of the outer ring 71 of the double row tapered roller bearing 70, the outer ring 71 is caused by a load load. When the shape of the outer peripheral surface is deformed in a wave shape in the circumferential direction, the influence of the deformation on the fitting surface can be suppressed, and the creep between the outer ring 71 and the housing can be suppressed without increasing the number of parts. Occurrence can be prevented.

また、外輪７１とハウジングとのしめしろを大きくする必要がないので、外輪７１の外輪軌道面７１ａに発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   In addition, since it is not necessary to increase the interference between the outer ring 71 and the housing, it is possible to avoid excessive circumferential stress generated on the outer ring raceway surface 71a of the outer ring 71. Assemblability can be improved.

（第８実施形態）
本発明の第８実施形態である車両用ハブユニット８０は、図９に示すように、ハウジングとしてのナックル８６と軸としてのハブ８７との間に、第６実施形態の円すいころ軸受６０を２個組み込んだものである。外輪６１は、締まりばめ又はすき間ばめによりナックル８６に嵌め込まれ、内輪６２は、締まりばめ又はすき間ばめによりハブ８７に嵌め込まれる。また、各内輪６２間には内輪間座８５が介装されている。
その他の構成及び作用効果については、第６実施形態と同様である。なお、本実施形態は、内輪回転タイプを例示しているが、外輪回転タイプに適用してもよい。 (Eighth embodiment)
As shown in FIG. 9, the vehicle hub unit 80 according to the eighth embodiment of the present invention includes two tapered roller bearings 60 according to the sixth embodiment between a knuckle 86 as a housing and a hub 87 as a shaft. It is one that has been incorporated. The outer ring 61 is fitted into the knuckle 86 by an interference fit or clearance fit, and the inner ring 62 is fitted into the hub 87 by an interference fit or clearance fit. An inner ring spacer 85 is interposed between the inner rings 62.
About another structure and an effect, it is the same as that of 6th Embodiment. In addition, although this embodiment has illustrated the inner ring | wheel rotation type, you may apply to an outer ring | wheel rotation type.

（第９実施形態）
本発明の第９実施形態である車両用ハブユニット９０は、図１０に示すように、ハウジングとしてのナックル９６と軸としてのハブ９７との間に、複列円すいころ軸受９８を組み込んだものであり、所謂、第１世代のハブユニットに適用された例である。複列円すいころ軸受９８は、内周面に一対の外輪軌道面９１ａを有する単一の部材である外輪９１と、外周面に内輪軌道面９２ａを有する一対の内輪９２と、一対の外輪軌道面９１ａと一対の内輪軌道面９２ａとの間に周方向に転動自在に配置される複列の円すいころ９３とを備える。複列円すいころ軸受９８は、外輪９１が、締まりばめ又はすき間ばめによりナックル９６に固定され、一対の内輪９２が締まりばめ又はすき間ばめによりハブ９７に固定された状態で用いられる。 (Ninth embodiment)
As shown in FIG. 10, a vehicle hub unit 90 according to the ninth embodiment of the present invention incorporates a double row tapered roller bearing 98 between a knuckle 96 as a housing and a hub 97 as a shaft. This is an example applied to a so-called first generation hub unit. The double row tapered roller bearing 98 includes an outer ring 91 that is a single member having a pair of outer ring raceway surfaces 91a on the inner peripheral surface, a pair of inner rings 92 having an inner ring raceway surface 92a on the outer peripheral surface, and a pair of outer ring raceway surfaces. A double row tapered roller 93 is provided between 91a and the pair of inner ring raceway surfaces 92a so as to be freely rollable in the circumferential direction. The double-row tapered roller bearing 98 is used in a state where the outer ring 91 is fixed to the knuckle 96 by interference fit or clearance fit, and the pair of inner rings 92 is fixed to the hub 97 by interference fit or clearance fit.

そして、軸方向において外輪軌道面９１ａに重なる外輪９１の外周面の一対の外輪軌道面位置ｂには、略矩形断面の周方向溝９４が列毎に周方向全周に亘って設けられている。この周方向溝９４は、外輪９１がナックル９６に固定された状態において、ナックル９６と非接触に維持される。また、各周方向溝９４は、外輪軌道面位置ｂ内に形成されればよく、外輪軌道面９１ａの軸方向寸法以下であればよい。また、周方向溝９４は、外輪９１の一対の外輪軌道面位置ｂにそれぞれ形成されているが、一方のみに形成されてもよい。この場合、負荷の大きくかかる側の外輪軌道面位置ｂに周方向溝９４を形成するのが好ましい。更に、本実施形態は、内輪回転タイプを例示しているが、外輪回転タイプに適用してもよい。
その他の構成及び作用については、第７実施形態のものと同様である。 A pair of outer ring raceway surface positions b on the outer peripheral surface of the outer ring 91 overlapping the outer ring raceway surface 91a in the axial direction is provided with circumferential grooves 94 having a substantially rectangular cross section over the entire circumference in each row. . The circumferential groove 94 is kept out of contact with the knuckle 96 in a state where the outer ring 91 is fixed to the knuckle 96. Each circumferential groove 94 only needs to be formed in the outer ring raceway surface position b, and may be equal to or smaller than the axial dimension of the outer ring raceway surface 91a. Further, although the circumferential grooves 94 are respectively formed at the pair of outer ring raceway surface positions b of the outer ring 91, they may be formed only on one side. In this case, it is preferable to form the circumferential groove 94 at the outer ring raceway surface position b on the side where a large load is applied. Furthermore, although this embodiment has illustrated the inner ring | wheel rotation type, you may apply to an outer ring | wheel rotation type.
Other configurations and operations are the same as those of the seventh embodiment.

（第１０実施形態）
本発明の第１０実施形態である円すいころ軸受１００は、第１実施形態の円すいころ軸受１０が、内輪１２の内周面の内輪軌道面１２ａ位置に矩形断面の周方向溝１４を設けているのに対して、図１１に示すように、内輪１２の内周面の内輪軌道面位置ａに、該軌道面１２ａと平行な底面を有する周方向溝１０４を設けて、該周方向溝１０４の底面と軌道面１２ａとの間の肉厚ｔを一定にしている。
その他の構成及び作用については、第１実施形態のものと同様である。 (10th Embodiment)
In the tapered roller bearing 100 according to the tenth embodiment of the present invention, the tapered roller bearing 10 according to the first embodiment is provided with a circumferential groove 14 having a rectangular cross section at the position of the inner ring raceway surface 12 a on the inner circumferential surface of the inner ring 12. On the other hand, as shown in FIG. 11, a circumferential groove 104 having a bottom surface parallel to the raceway surface 12 a is provided at the inner raceway surface position a on the inner circumference surface of the inner ring 12. The wall thickness t between the bottom surface and the raceway surface 12a is made constant.
Other configurations and operations are the same as those in the first embodiment.

（第１１実施形態）
本発明の第１１実施形態である円すいころ軸受１１０は、第６実施形態の円すいころ軸受６０が、外輪６１の外周面の外輪軌道面６１ａ位置に矩形断面の周方向溝６４を設けているのに対して、図１２に示すように、外輪６１の外周面の外輪軌道面位置ｂに、該軌道面６１ａと平行な底面を有する周方向溝１１４を設けて、該周方向溝１１４の底面と軌道面６１ａとの間の肉厚ｔを一定にしている。
その他の構成及び作用については、第６実施形態のものと同様である。 (Eleventh embodiment)
In the tapered roller bearing 110 according to the eleventh embodiment of the present invention, the tapered roller bearing 60 according to the sixth embodiment is provided with a circumferential groove 64 having a rectangular cross section at the position of the outer ring raceway surface 61 a on the outer circumferential surface of the outer ring 61. On the other hand, as shown in FIG. 12, a circumferential groove 114 having a bottom surface parallel to the raceway surface 61 a is provided at the outer ring raceway surface position b on the outer circumferential surface of the outer ring 61, and the bottom surface of the circumferential groove 114 is The wall thickness t between the raceway surface 61a is constant.
Other configurations and operations are the same as those of the sixth embodiment.

（第１２実施形態）
本発明の第１２実施形態である深溝玉軸受１２０は、図１３に示すように、内周面に外輪軌道面１２１ａを有する外輪１２１と、外周面に内輪軌道面１２２ａを有する内輪１２２と、外輪軌道面１２１ａと内輪軌道面１２２ａとの間に周方向に転動自在に配置される複数の玉１２３とを備える。深溝玉軸受１２０は、外輪１２１が締まりばめ又はすき間ばめによりハウジング１２７に固定され、内輪１２２が締まりばめ又はすき間ばめにより軸１２６に固定された状態で使用される。 (Twelfth embodiment)
As shown in FIG. 13, a deep groove ball bearing 120 according to a twelfth embodiment of the present invention includes an outer ring 121 having an outer ring raceway surface 121a on an inner peripheral surface, an inner ring 122 having an inner ring raceway surface 122a on an outer peripheral surface, and an outer ring. A plurality of balls 123 are provided between the raceway surface 121a and the inner ring raceway surface 122a so as to be freely rollable in the circumferential direction. The deep groove ball bearing 120 is used in a state in which the outer ring 121 is fixed to the housing 127 by interference fit or clearance fit and the inner ring 122 is fixed to the shaft 126 by interference fit or clearance fit.

軸方向において外輪軌道面１２１ａと重なる外輪１２１の外周面の外輪軌道面位置ｂには、ハウジング１２７と非接触である周方向溝１２４が周方向全周に亘って設けられている。この周方向溝１２４は、図１４（ａ）に示すように、頂点が湾曲形状の三角形断面を有しており、また、周方向溝１２４の最大深さＤｅは５〜２０μｍと微小に設定されている。   A circumferential groove 124 that is not in contact with the housing 127 is provided over the entire circumference in the outer ring raceway surface position b of the outer ring 121 that overlaps the outer ring raceway surface 121a in the axial direction. As shown in FIG. 14A, the circumferential groove 124 has a triangular cross section with a curved vertex, and the maximum depth De of the circumferential groove 124 is set to a very small value of 5 to 20 μm. ing.

このように、本実施形態では、深溝玉軸受１２０の外輪１２１の外周面の外輪軌道面位置ｂに、ハウジング１２７と非接触で、頂点が湾曲形状の三角形断面の周方向溝１２４が形成されるので、荷重負荷によって、外輪１２１の外周面の形状が円周方向に波状に変形した際に、この変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、外輪１２１とハウジング１２７との間のクリープの発生を防止することができる。   As described above, in the present embodiment, the circumferential groove 124 having a triangular cross section with a curved vertex is formed in the outer ring raceway surface position b on the outer circumferential surface of the outer ring 121 of the deep groove ball bearing 120 in a non-contact manner with the housing 127. Therefore, when the shape of the outer peripheral surface of the outer ring 121 is deformed into a wave shape in the circumferential direction due to a load, the influence of this deformation on the fitting surface can be suppressed, and the outer ring 121 is not increased without increasing the number of parts. And creeping between the housing 127 and the housing 127 can be prevented.

また、外輪１２１とハウジング１２７との間のしめしろを大きくする必要がないので、外輪１２１の外輪軌道面１２１ａに発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   Further, since it is not necessary to increase the interference between the outer ring 121 and the housing 127, it is possible to avoid excessive circumferential stress generated on the outer ring raceway surface 121a of the outer ring 121. Durability and assemblability can be improved.

更に、周方向溝１２４の形状を頂点が湾曲形状の三角形断面とし、しかも周方向溝１２４の最大深さＤｅを５〜２０μｍと微小に設定しているので、矩形断面の周方向溝に比べて、軸受の剛性低下を抑制することができる。なお、周方向溝１２４の断面形状は、頂点が湾曲形状の三角形断面に代えて、図１４（ｂ）に示すように、円弧断面としてもよく、或いは図１４（ｃ）に示すように、短辺側両隅部が湾曲形状の台形断面としてもよい。   Furthermore, since the circumferential groove 124 has a triangular cross section with a curved vertex, and the maximum depth De of the circumferential groove 124 is set to a very small value of 5 to 20 μm, it is smaller than the circumferential groove having a rectangular section. Thus, it is possible to suppress a decrease in bearing rigidity. The cross-sectional shape of the circumferential groove 124 may be an arc cross-section as shown in FIG. 14 (b) instead of a triangular cross-section with a curved vertex, or short as shown in FIG. 14 (c). Both side corners may have a trapezoidal cross section having a curved shape.

（第１３実施形態）
本発明の第１３実施形態である深溝玉軸受１３０は、図１５に示すように、内周面に外輪軌道面１３１ａを有する外輪１３１と、外周面に内輪軌道面１３２ａを有する内輪１３２と、外輪軌道面１３１ａと内輪軌道面１３２ａとの間に周方向に転動自在に配置される複数の玉１３３とを備える。深溝玉軸受１３０は、外輪１３１が締まりばめ又はすき間ばめによりハウジング１３７に固定され、内輪１３２が締まりばめ又はすき間ばめにより軸１３６に固定された状態で使用される。 (13th Embodiment)
As shown in FIG. 15, a deep groove ball bearing 130 according to a thirteenth embodiment of the present invention includes an outer ring 131 having an outer ring raceway surface 131a on an inner peripheral surface, an inner ring 132 having an inner ring raceway surface 132a on an outer peripheral surface, and an outer ring. A plurality of balls 133 are provided between the raceway surface 131a and the inner ring raceway surface 132a so as to be freely rollable in the circumferential direction. The deep groove ball bearing 130 is used in a state in which the outer ring 131 is fixed to the housing 137 by interference fit or clearance fit, and the inner ring 132 is fixed to the shaft 136 by interference fit or clearance fit.

軸方向において内輪軌道面１３２ａと重なる内輪１３２の内周面の内輪軌道面位置ａには、軸１３６と非接触である周方向溝１３４が周方向全周に亘って設けられている。この周方向溝１３４は、第１２実施形態と同様に、頂点が湾曲形状の三角形断面を有しており、また、周方向溝１３４の最大深さＤｅは５〜２０μｍと微小に設定されている。   A circumferential groove 134 that is not in contact with the shaft 136 is provided over the entire circumference in the inner ring raceway surface position a on the inner circumferential surface of the inner ring 132 that overlaps the inner ring raceway surface 132a in the axial direction. Similar to the twelfth embodiment, the circumferential groove 134 has a triangular cross section with a curved vertex, and the maximum depth De of the circumferential groove 134 is set to be as small as 5 to 20 μm. .

このように、本実施形態では、深溝玉軸受１３０の内輪１３２の内周面の内輪軌道面位置ａに、軸１３６と非接触で、頂点が湾曲形状の三角形断面の周方向溝１３４が形成されるので、荷重負荷によって、内輪１３２の内周面の形状が円周方向に波状に変形した際に、この変形が嵌めあい面に及ぼす影響を抑制することができ、部品点数を増やすことなく、内輪１３２と軸１３６との間のクリープの発生を防止することができる。   Thus, in the present embodiment, the circumferential groove 134 having a triangular cross section with a curved shape at the apex is formed in the inner ring raceway surface position a on the inner circumferential surface of the inner ring 132 of the deep groove ball bearing 130 in a non-contact manner. Therefore, when the shape of the inner peripheral surface of the inner ring 132 is deformed in a wave shape in the circumferential direction due to a load, it is possible to suppress the influence of this deformation on the fitting surface, without increasing the number of parts, The occurrence of creep between the inner ring 132 and the shaft 136 can be prevented.

また、内輪１３２と軸１３６との間のしめしろを大きくする必要がないので、内輪１３２の内輪軌道面１３２ａに発生する円周方向応力が過大になるのを回避することができ、これにより、耐久性及び組立性の向上を図ることができる。   Further, since it is not necessary to increase the interference between the inner ring 132 and the shaft 136, it is possible to avoid excessive circumferential stress generated on the inner ring raceway surface 132a of the inner ring 132. Durability and assemblability can be improved.

更に、周方向溝１３４の形状を頂点が湾曲形状の三角形断面とし、しかも周方向溝１３４の深さＤｅを５〜２０μｍと微小に設定しているので、矩形断面の周方向溝に比べて、軸受の剛性低下を抑制することができる。なお、周方向溝１３４の断面形状は、第１２実施形態と同様に、頂点が湾曲形状の三角形断面に代えて、円弧断面としてもよく、或いは短辺側両隅部が湾曲形状の台形断面としてもよい。   Furthermore, since the circumferential groove 134 has a triangular cross section with a curved vertex, and the depth De of the circumferential groove 134 is set to 5 to 20 μm, compared to the circumferential groove having a rectangular cross section, A reduction in the rigidity of the bearing can be suppressed. As in the twelfth embodiment, the circumferential groove 134 may have a circular arc cross section instead of a triangular cross section with a curved top, or a trapezoidal cross section with curved corners on both short sides. Also good.

なお、本発明の円すいころ軸受及び深溝玉軸受は、本実施形態に限定されるものでなく、適宜な変形、改良等が可能である。また、上記実施形態は、実施可能な範囲において組み合わせて適用されてもよい。例えば、円すいころ軸受の周方向溝の形状も、深溝玉軸受のものと同様、円弧断面、短辺側両隅部が湾曲形状の台形断面、頂点が湾曲形状の三角形断面のいずれかであってもよい。   The tapered roller bearing and the deep groove ball bearing of the present invention are not limited to this embodiment, and appropriate modifications, improvements, and the like are possible. Moreover, the said embodiment may be applied combining in the range which can be implemented. For example, the shape of the circumferential groove of the tapered roller bearing is the same as that of the deep groove ball bearing, either an arc cross-section, a trapezoidal cross-section with curved corners at the short side corners, or a triangular cross-section with a curved apex. Also good.

上記実施形態では、内輪側あるいは外輪側に周方向溝を設けた例を示したが、内輪側及び外輪側の両方に周方向溝を設けるようにしてもよく、周方向溝の数は特に限定されない。また、周方向溝は、本実施形態のように全周に亘って設けられてもよく、或いは、周方向に部分的に設けるようにしてもよい。   In the above embodiment, an example in which circumferential grooves are provided on the inner ring side or the outer ring side is shown. However, circumferential grooves may be provided on both the inner ring side and the outer ring side, and the number of circumferential grooves is particularly limited. Not. Further, the circumferential groove may be provided over the entire circumference as in the present embodiment, or may be provided partially in the circumferential direction.

また、上記実施形態は、円すいころ軸受或いは深溝玉軸受に周方向溝を形成しているが、例えば、従来の円すいころ軸受１Ａ（図１８参照）を用いて、図１６に示すように、軸方向において内輪軌道面と重なる軸１４６の外周面の内輪軌道面位置に周方向溝１４６ａが形成されてもよく、或いは図１７に示すように、軸方向において外輪軌道面と重なるハウジング１４７の内周面の外輪軌道面位置に周方向溝１４７ａが形成されてもよい。この場合にも、上述した実施形態と同様の効果を得ることができる。   Moreover, although the said embodiment forms the circumferential groove | channel in the tapered roller bearing or the deep groove ball bearing, for example, as shown in FIG. 16 using a conventional tapered roller bearing 1A (see FIG. 18), the shaft A circumferential groove 146a may be formed at the position of the inner ring raceway surface of the outer circumferential surface of the shaft 146 that overlaps the inner ring raceway surface in the direction, or the inner circumference of the housing 147 that overlaps the outer ring raceway surface in the axial direction as shown in FIG. A circumferential groove 147a may be formed at the outer ring raceway surface position of the surface. Also in this case, the same effect as the above-described embodiment can be obtained.

本発明の第１実施形態である円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the tapered roller bearing which is 1st Embodiment of this invention. 本発明の第２実施形態である複列円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the double row tapered roller bearing which is 2nd Embodiment of this invention. 本発明の第３実施形態である車両用ハブユニットを示す要部断面図である。It is principal part sectional drawing which shows the hub unit for vehicles which is 3rd Embodiment of this invention. 本発明の第４実施形態である車両用ハブユニットを示す要部断面図である。It is principal part sectional drawing which shows the hub unit for vehicles which is 4th Embodiment of this invention. 本発明の第５実施形態である車両用ハブユニットを示す要部断面図である。It is principal part sectional drawing which shows the hub unit for vehicles which is 5th Embodiment of this invention. 本発明の第５実施形態の変形例である車両用ハブユニットを示す要部断面図である。It is principal part sectional drawing which shows the hub unit for vehicles which is a modification of 5th Embodiment of this invention. 本発明の第６実施形態である円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the tapered roller bearing which is 6th Embodiment of this invention. 本発明の第７実施形態である複列円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the double row tapered roller bearing which is 7th Embodiment of this invention. 本発明の第８実施形態である車両用ハブユニットを示す要部断面図である。It is principal part sectional drawing which shows the hub unit for vehicles which is 8th Embodiment of this invention. 本発明の第９実施形態である車両用ハブユニットを示す要部断面図である。It is principal part sectional drawing which shows the hub unit for vehicles which is 9th Embodiment of this invention. 本発明の第１０実施形態である円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the tapered roller bearing which is 10th Embodiment of this invention. 本発明の第１１実施形態である円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the tapered roller bearing which is 11th Embodiment of this invention. 本発明の第１２実施形態である深溝玉軸受を示す要部断面図である。It is principal part sectional drawing which shows the deep groove ball bearing which is 12th Embodiment of this invention. （ａ）は周方向溝の拡大断面図であり、（ｂ）及び（ｃ）は周方向溝の変形例である。(A) is an expanded sectional view of a circumferential groove, (b) and (c) are modified examples of the circumferential groove. 本発明の第１３実施形態である深溝玉軸受を示す要部断面図である。It is principal part sectional drawing which shows the deep groove ball bearing which is 13th Embodiment of this invention. 軸に周方向溝を形成した例を示す要部断面図である。It is principal part sectional drawing which shows the example which formed the circumferential direction groove | channel in the axis | shaft. ハウジングに周方向溝を形成した例を示す要部断面図である。It is principal part sectional drawing which shows the example which formed the circumferential direction groove | channel in the housing. 従来の円すいころ軸受を示す要部断面図である。It is principal part sectional drawing which shows the conventional tapered roller bearing.

符号の説明Explanation of symbols

１０ 円すいころ軸受
１１ａ 外輪軌道面
１１ 外輪
１２ａ 内輪軌道面
１２ 内輪
１３ 円すいころ
１４ 周方向溝
２０ 複列円すいころ軸受
３０ 車両用ハブユニット
１２０ 深溝玉軸受
１２１ａ 外輪軌道面
１２１ 外輪
１２２ａ 内輪軌道面
１２２ 内輪
１２３ 玉
１２４ 周方向溝
１２６ 軸
１２７ ハウジング DESCRIPTION OF SYMBOLS 10 Tapered roller bearing 11a Outer ring raceway surface 11 Outer ring 12a Inner ring raceway surface 12 Inner ring 13 Tapered roller 14 Circumferential groove 20 Double row tapered roller bearing 30 Vehicle hub unit 120 Deep groove ball bearing 121a Outer raceway surface 121 Outer ring 122a Inner ring raceway surface 122 Inner ring 123 ball 124 circumferential groove 126 shaft 127 housing

Claims (5)

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周方向に転動自在に配置される複数の円すいころとを備え、前記内輪が締まりばめ又はすき間ばめにより軸に固定され、前記外輪が締まりばめ又はすき間ばめによりハウジングに固定された状態で使用される円すいころ軸受であって、
前記内輪の内周面の内輪軌道面位置と前記外輪の外周面の外輪軌道面位置のいずれか一方の軌道面位置には、該軌道面位置と対向する前記軸又は前記ハウジングと非接触な周方向溝が形成されることを特徴とする円すいころ軸受。 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 tapered rollers disposed so as to be freely rollable in a circumferential direction between the outer ring raceway surface and the inner ring raceway surface. A tapered roller bearing used in a state where the inner ring is fixed to the shaft by interference fit or clearance fit, and the outer ring is fixed to the housing by interference fit or clearance fit,
One of the inner ring raceway surface position on the inner peripheral surface of the inner ring and the outer ring raceway surface position on the outer peripheral surface of the outer ring has a circumference that is not in contact with the shaft or the housing facing the raceway surface position. A tapered roller bearing in which a directional groove is formed. 前記外輪と前記内輪は、一対の外輪軌道面と一対の内輪軌道面をそれぞれ備え、
前記円すいころは前記一対の外輪軌道面と前記一対の内輪軌道面間に配置される複列の円すいころであって、
前記外輪又は前記内輪は、前記一対の外輪軌道面又は前記一対の内輪軌道面を単一の部材によって形成し、
前記周方向溝は、前記内輪の内周面の一対の内輪軌道面位置、及び前記外輪の外周面の一対の外輪軌道面位置の少なくとも一つの軌道面位置に形成されることを特徴とする請求項１に記載の円すいころ軸受。 The outer ring and the inner ring each include a pair of outer ring raceway surfaces and a pair of inner ring raceway surfaces,
The tapered roller is a double row tapered roller disposed between the pair of outer ring raceway surfaces and the pair of inner ring raceway surfaces,
The outer ring or the inner ring is formed of the pair of outer ring raceway surfaces or the pair of inner ring raceway surfaces by a single member,
The circumferential groove is formed at at least one track surface position of a pair of inner ring raceway surface positions on an inner peripheral surface of the inner ring and a pair of outer ring raceway surface positions on an outer peripheral surface of the outer ring. The tapered roller bearing according to Item 1. 請求項１又は２に記載の円すいころ軸受を組み込んだことを特徴とする車両用ハブユニット。   A hub unit for a vehicle, wherein the tapered roller bearing according to claim 1 is incorporated. 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周方向に転動自在に配置される複数の玉とを備え、前記内輪が締まりばめ又はすき間ばめにより軸に固定され、前記外輪が締まりばめ又はすき間ばめによりハウジングに固定された状態で使用される深溝玉軸受であって、
前記内輪の内周面の内輪軌道面位置と前記外輪の外周面の外輪軌道面位置のいずれか一方の軌道面位置には、該軌道面位置と対向する前記軸又は前記ハウジングと非接触である、円弧断面、短辺側両隅部が湾曲形状の台形断面、頂点が湾曲形状の三角形断面のいずれかの周方向溝が形成されることを特徴とする深溝玉軸受。 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 balls arranged so as to be rollable in a circumferential direction between the outer ring raceway surface and the inner ring raceway surface; A deep groove ball bearing used in a state where the inner ring is fixed to the shaft by interference fit or clearance fit, and the outer ring is fixed to the housing by interference fit or clearance fit,
Either the inner ring raceway surface position on the inner circumferential surface of the inner ring or the outer ring raceway surface position on the outer circumferential surface of the outer ring is not in contact with the shaft or the housing facing the raceway surface position. A deep groove ball bearing characterized in that a circumferential groove is formed in any one of a circular cross section, a trapezoidal cross section with curved corners on both short sides, and a triangular cross section with a curved top. 前記周方向溝の最大深さが５〜２０μｍであることを特徴とする請求項４に記載の深溝玉軸受。   The deep groove ball bearing according to claim 4, wherein a maximum depth of the circumferential groove is 5 to 20 μm.
JP2005269920A 2005-09-16 2005-09-16 Tapered roller bearing, deep groove ball bearing, and hub unit for vehicle Withdrawn JP2007078137A (en)

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