JP6432178B2 - Tapered roller bearings - Google Patents

Tapered roller bearings Download PDF

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JP6432178B2
JP6432178B2 JP2014128576A JP2014128576A JP6432178B2 JP 6432178 B2 JP6432178 B2 JP 6432178B2 JP 2014128576 A JP2014128576 A JP 2014128576A JP 2014128576 A JP2014128576 A JP 2014128576A JP 6432178 B2 JP6432178 B2 JP 6432178B2
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diameter
tapered roller
ring
roller bearing
diameter side
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JP2016008642A (en
JP2016008642A5 (en
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誠 黄金井
誠 黄金井
青木　護
護 青木
俊一 清野
俊一 清野
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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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm

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

Description

本発明は、円錐ころ軸受、特に、自動車、鉄道車両、建設機械、工作機械、搬送装置、組立装置等に好適に使用可能な円錐ころ軸受に関する。 The present invention, tapered roller bearings, in particular, motor vehicles, railway vehicles, construction machinery, machine tools, conveying apparatus, and suitably usable tapered roller bearing assembling device and the like.

従来、モーメント剛性を必要とする場合に選定される転がり軸受としては、アンギュラ玉軸受が考えられる。   Conventionally, as a rolling bearing selected when moment rigidity is required, an angular ball bearing can be considered.

また、円錐ころ軸受として、内輪の小鍔を不要とし、その分だけころ長さを長くすることで、負荷容量を大きくしたものが知られている（例えば、特許文献１参照）。また、特許文献１の円錐ころ軸受では、保持器のポケットの外周側および内周側の開口縁部に、突部を設けて、ころと保持器とを一体化して、取り扱い性を向上させている。   Further, as a tapered roller bearing, there is known a tapered roller bearing that does not require a small collar on the inner ring and increases the load capacity by increasing the roller length accordingly (see, for example, Patent Document 1). Further, in the tapered roller bearing of Patent Document 1, protrusions are provided on the opening edge on the outer peripheral side and inner peripheral side of the pocket of the cage, and the roller and the cage are integrated to improve handling. Yes.

さらに、特許文献２に記載の円錐ころ軸受では、保持器の大径側リング部は、内輪の大径側鍔部と対応する断面形状を有し、大径側鍔部の大径側内側端面と向かい合わせで対向する大径側外側端面を備え、さらに、この大径側外側端面には、小径側外側端面から連通する油導入通路が開口している。   Furthermore, in the tapered roller bearing described in Patent Document 2, the large-diameter side ring portion of the cage has a cross-sectional shape corresponding to the large-diameter side flange portion of the inner ring, and the large-diameter side inner end surface of the large-diameter side flange portion. The large-diameter side outer end face is opposed to the large-diameter side, and an oil introduction passage communicating from the small-diameter side outer end face is opened in the large-diameter side outer end face.

特開２００７−３２６７９号公報JP 2007-32679 A 特開２０１２−２４１８７３号公報JP 2012-241873 A

しかしながら、アンギュラ玉軸受において、さらなる高モーメント剛性や長寿命の要求に対応するには、軸受サイズが大きくなってしまい、軸受サイズの維持又は縮小という要求に対応する為には、限界がある。
更に、最近、変速機用として使用される軸受では、高負荷容量で、かつ、変速機のコンパクト化に対応できるもの、つまり、軸受サイズを変更することなく、従来と同等以上の機能であることが求められる。 However, in the angular ball bearing, in order to meet the demand for higher moment rigidity and longer life, the bearing size becomes large, and there is a limit to meet the demand for maintaining or reducing the bearing size.
Furthermore, recently, a bearing used for a transmission has a high load capacity and can cope with the downsizing of the transmission, that is, has a function equal to or higher than that of a conventional one without changing the bearing size. Is required.

一方、特許文献１及び２に記載の円錐ころ軸受では、接触角について考慮されておらず、図示された円錐ころ軸受の接触角では、ラジアル剛性は高いが、高いモーメント剛性が得られないと考えられる。
また、特許文献２に記載の円錐ころ軸受において、保持器の大径側リング部の断面形状は、焼き付き対策として油導入通路を形成するための形状となっており、大径側リング部の肉厚が厚く、内輪大鍔との干渉を考慮しておらず、接触角が急勾配時の円錐ころの挿入性についても考慮されていない。 On the other hand, in the tapered roller bearings described in Patent Documents 1 and 2, the contact angle is not considered, and the contact angle of the illustrated tapered roller bearing is high in radial rigidity, but it is considered that high moment rigidity cannot be obtained. It is done.
Moreover, in the tapered roller bearing described in Patent Document 2, the cross-sectional shape of the large-diameter side ring portion of the cage is a shape for forming an oil introduction passage as a measure against seizure, and the meat of the large-diameter side ring portion is Thickness is not taken into consideration, and interference with the inner ring collar is not taken into consideration, and insertion of the tapered roller when the contact angle is steep is not taken into consideration.

そこで本発明は前述の状況に鑑みてなされたものであり、その目的は、大径リング部の端部が外輪及び内輪と干渉するのを防止することができ、高モーメント剛性および長寿命を実現した円錐ころ軸受を提供することにある。   Therefore, the present invention has been made in view of the above-described situation, and the purpose thereof is to prevent the end of the large-diameter ring portion from interfering with the outer ring and the inner ring, and realize high moment rigidity and a long life. To provide a tapered roller bearing.

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、
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円錐ころと、
軸方向に離間した大径リング部及び小径リング部と、該大径リング部及び小径リング部との間を繋ぐ複数の柱部と、を有し、前記円錐ころを収容保持する複数のポケットを画成する樹脂製保持器と、
を備える円錐ころ軸受において、
前記円錐ころ軸受の接触角αが３５°〜５５°であり、
前記内輪は、大径側端部と小径側端部のうち、大径側端部にのみ鍔部が形成され、且つ、
前記樹脂製保持器の大径リング部は、軸方向へ延伸する端部を有し、
前記大径リング部の内周面には、該リング部の肉厚が前記柱部の肉厚よりも薄くなるように、切欠き部が設けられ、
前記切欠き部は、前記柱部における、前記円錐ころの転走面と対向する部分から前記大径リング部にかけて、前記柱部の一部を切欠いて形成されることを特徴とする円錐ころ軸受。
（２） 前記柱部は、前記ポケットの内径側の少なくとも一部において、０．２ｍｍ〜０．７ｍｍのかかり代とし、前記ポケットの内径側開口幅が前記円錐ころのころ大径より狭くなるように形成され、且つ、前記ポケットの外径側の少なくとも一部において、０．１ｍｍ〜０．５ｍｍのかかり代とし、前記ポケットの外径側開口幅が前記円錐ころのころ小径より狭くなるように形成されることを特徴とする（１）に記載の円錐ころ軸受。
（３） 前記切欠き部は、前記大径リング部の肉厚が前記柱部の肉厚よりも薄くなるように、第１の面、第２の面、及び第１及び第２の面を接続する第３の面によって構成されることを特徴とする（１）又は（２）に記載の円錐ころ軸受。
（４） 前記大径リング部の肉厚が前記柱部の肉厚の４０〜８０％であり、且つ、
前記柱部の肉厚が前記円錐ころのころ平均径の３０〜７０％であることを特徴とする（１）〜（３）のいずれかに記載の円錐ころ軸受。
（５） 前記保持器の傾斜角度は、３２°３０´以上５５°以下に設定されることを特徴とする（１）〜（４）のいずれかに記載の円錐ころ軸受。
（６） 前記外輪の大径側端部と前記内輪の小径側端部の少なくとも一方には、軸方向に延びる軸方向延長部が形成されることを特徴とする（１）〜（５）のいずれかに記載の円錐ころ軸受。 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 the inner circumferential surface;
An inner ring having an inner ring raceway surface on the outer peripheral surface;
A plurality of tapered rollers disposed between the outer ring raceway surface and the inner ring raceway surface in a freely rollable manner;
A plurality of pockets for accommodating and holding the tapered rollers, and a large-diameter ring portion and a small-diameter ring portion that are spaced apart in the axial direction, and a plurality of pillar portions that connect the large-diameter ring portion and the small-diameter ring portion. A resin cage to define,
In a tapered roller bearing comprising:
The tapered roller bearing has a contact angle α of 35 ° to 55 °,
The inner ring has a flange formed only at the large-diameter end among the large-diameter end and the small-diameter end, and
The large-diameter ring portion of the resin cage can have a end which extends in the axial direction,
A cutout portion is provided on the inner peripheral surface of the large-diameter ring portion so that the thickness of the ring portion is thinner than the thickness of the column portion,
The notch is in the pillar portion, said from rolling surface opposed to part of the tapered roller toward the large diameter ring portion, tapered roller bearing, characterized in Rukoto formed by notching a portion of the pillar portion .
(2) The column portion has a margin of 0.2 mm to 0.7 mm in at least a part of the inner diameter side of the pocket so that the inner diameter side opening width of the pocket is smaller than the large diameter of the tapered roller. And at least a part of the outer diameter side of the pocket is a margin of 0.1 mm to 0.5 mm, and the opening diameter of the outer diameter side of the pocket is narrower than the small roller diameter of the tapered roller. The tapered roller bearing according to (1), wherein the tapered roller bearing is formed .
(3 ) The notch portion includes the first surface, the second surface, and the first and second surfaces so that the thickness of the large-diameter ring portion is thinner than the thickness of the column portion. The tapered roller bearing according to (1) or (2) , wherein the tapered roller bearing is configured by a third surface to be connected.
( 4 ) The thickness of the large-diameter ring portion is 40 to 80% of the thickness of the column portion, and
The tapered roller bearing according to any one of (1) to (3), wherein a thickness of the column portion is 30 to 70% of an average roller diameter of the tapered roller.
( 5 ) The tapered roller bearing according to any one of (1) to ( 4 ), wherein an inclination angle of the cage is set to 32 ° 30 ′ or more and 55 ° or less.
( 6 ) The axial direction extension part extended in an axial direction is formed in at least one of the large diameter side edge part of the said outer ring | wheel, and the small diameter side edge part of the said inner ring | wheel of (1)-( 5 ) characterized by the above-mentioned. The tapered roller bearing according to any one of the above.

以上のように、本発明に係る円錐ころ軸受によれば、内輪には、大径側端部と小径側端部のうち、該大径側端部にのみ鍔部が形成されるので、ころ長さを最大限長くすることが可能となり、負荷容量を大きくとることができ、高モーメント剛性および長寿命化を図ることができる。また、円錐ころ軸受の接触角αが３５°〜５５°であるので、モーメント剛性をさらに向上することができる。特に、軸受間距離が短い、具体的には、軸受間距離が軸受の組立幅Ｔの４倍以下の場合に、作用点間距離を長くすることができ、軸受のモーメント剛性を向上する上で有効である。
また、樹脂製保持器の大径リング部は、軸方向へ延伸する端部を有するので、大径リング部の端部が外輪及び内輪と干渉するのを防止することができ、また、保持器大径側の強度を向上することもできる。 As described above, according to the tapered roller bearing according to the present invention, the inner ring is formed with the flange portion only at the large diameter side end portion of the large diameter side end portion and the small diameter side end portion. The length can be maximized, the load capacity can be increased, and high moment rigidity and a long life can be achieved. Further, since the contact angle α of the tapered roller bearing is 35 ° to 55 °, the moment rigidity can be further improved. In particular, when the distance between the bearings is short, specifically, when the distance between the bearings is not more than 4 times the assembly width T of the bearing, the distance between the operating points can be increased, and the moment rigidity of the bearing is improved. It is valid.
In addition, since the large-diameter ring portion of the resin cage has an end portion extending in the axial direction, it is possible to prevent the end portion of the large-diameter ring portion from interfering with the outer ring and the inner ring. The strength on the large diameter side can also be improved.

（ａ）は、本発明の第１実施形態に係る円錐ころ軸受の断面図であり、（ｂ）は、円錐ころを示す図である。(A) is sectional drawing of the tapered roller bearing which concerns on 1st Embodiment of this invention, (b) is a figure which shows a tapered roller. 図１の樹脂製保持器の断面図である。It is sectional drawing of the resin cage of FIG. （ａ）は、図１の樹脂製保持器の斜視図であり、（ｂ）は、（ａ）の要部拡大斜視図である。(A) is a perspective view of the resin cage shown in FIG. 1, and (b) is an enlarged perspective view of a main part of (a). （ａ）は、図１のＩＶ−ＩＶ線に沿った断面図であり、（ｂ）は、図１のＩＶ´−ＩＶ´線に沿った断面図である。(A) is sectional drawing along the IV-IV line of FIG. 1, (b) is sectional drawing along the IV'-IV 'line of FIG. 参考例の円錐ころ軸受の断面図である。It is sectional drawing of the tapered roller bearing of a reference example. 第１実施形態の変形例に係る円錐ころ軸受の断面図である。It is sectional drawing of the tapered roller bearing which concerns on the modification of 1st Embodiment. 本発明の第２実施形態に係る円錐ころ軸受の断面図である。It is sectional drawing of the tapered roller bearing which concerns on 2nd Embodiment of this invention. 本発明の第３実施形態に係る円錐ころ軸受の断面図である。It is sectional drawing of the tapered roller bearing which concerns on 3rd Embodiment of this invention.

以下、本発明の各実施形態に係る円錐ころ軸受について、図面に基づき詳細に説明する。   Hereinafter, tapered roller bearings according to embodiments of the present invention will be described in detail with reference to the drawings.

（第１実施形態）
図１に示すように、第１実施形態の円錐ころ軸受１は、内周面に外輪軌道面２ａを有する外輪２と、外周面に内輪軌道面３ａを有する内輪３と、外輪軌道面２ａと内輪軌道面３ａとの間に転動自在に配置される複数の円錐ころ４と、複数の円錐ころ４を所定の間隔で収容保持する複数のポケットＰを画成する樹脂製保持器１０と、を有する。 (First embodiment)
As shown in FIG. 1, the tapered roller bearing 1 of the first embodiment includes an outer ring 2 having an outer ring raceway surface 2a on an inner peripheral surface, an inner ring 3 having an inner ring raceway surface 3a on an outer peripheral surface, and an outer ring raceway surface 2a. A plurality of tapered rollers 4 that are rotatably arranged between the inner ring raceway surface 3a, and a resin cage 10 that defines a plurality of pockets P that accommodate and hold the plurality of tapered rollers 4 at a predetermined interval; Have

外輪２に形成された外輪軌道面２ａは、外輪２の内周面に小径側から大径側に向かうに従って内径が次第に大きくなるように設けられている。   The outer ring raceway surface 2a formed on the outer ring 2 is provided on the inner circumferential surface of the outer ring 2 so that the inner diameter gradually increases from the small diameter side toward the large diameter side.

また、内輪３は、大径側端部に半径方向外方に突出して形成された大鍔３ｂを備え、小径側端部には鍔を備えていない。内輪軌道面３ａは、小径側から大径側に向かうに従って外径が次第に大きくなるように設けられている。大鍔３ｂは、円錐ころ４の大径側端面４ａと対向する外周縁から円弧状の面取り部を介して軸方向に延びる外周面を備え、この大鍔外周面が内輪外径を規定している。
さらに、外輪軌道面２ａ、内輪軌道面３ａ、及び円錐ころ４の転動面の少なくとも一つは、面圧を低減するように、クラウニング形状を有することが好ましい。 Further, the inner ring 3 includes a large flange 3b formed to protrude radially outward at an end portion on the large diameter side, and does not include a flange on the end portion on the small diameter side. The inner ring raceway surface 3a is provided such that the outer diameter gradually increases from the small diameter side toward the large diameter side. The large flange 3b includes an outer peripheral surface extending in the axial direction from the outer peripheral edge facing the large diameter side end surface 4a of the tapered roller 4 via an arc-shaped chamfered portion, and the large flange outer peripheral surface defines the inner ring outer diameter. Yes.
Furthermore, it is preferable that at least one of the outer ring raceway surface 2a, the inner ring raceway surface 3a, and the rolling surfaces of the tapered rollers 4 has a crowning shape so as to reduce the surface pressure.

内輪３の小径側端部には、軸方向に延びる軸方向延長部３ｃが設けられており、内輪軌道面３ａと軸方向延長部３ｃの外周面との間には、逃げ溝３ｄが形成されている。また、外輪２の大径側端部にも、軸方向に延びる軸方向延長部２ｂが設けられており、外輪軌道面２ａと軸方向延長部２ｂの内周面との間には、逃げ溝２ｃが形成されている。これら軸方向延長部２ｂ、３ｃを設けることで、軸受を装置へ組み付ける際の取付け性や位置決め性を向上させ、また、軌道輪の軸方向長さを延長することができるため、軸やハウジングへの組込み性を向上することができる。   An axial extension 3c extending in the axial direction is provided at the small diameter side end of the inner ring 3, and a clearance groove 3d is formed between the inner ring raceway surface 3a and the outer peripheral surface of the axial extension 3c. ing. An axial extension 2b extending in the axial direction is also provided at the large diameter side end of the outer ring 2, and a clearance groove is provided between the outer ring raceway surface 2a and the inner peripheral surface of the axial extension 2b. 2c is formed. By providing these axially extending portions 2b and 3c, it is possible to improve mountability and positioning when assembling the bearing to the device, and to extend the axial length of the bearing ring, so that the shaft and housing can be extended. Can be improved.

また、本実施形態の円錐ころ軸受１では、外輪軌道面２ａの接線と円錐ころ１の回転軸線とのなす角度である接触角αが４５°に設定されている。これにより、モーメント剛性を向上することができ、また、ころ長さを長くして負荷容量を大きくとることができ、高モーメント剛性及び長寿命化を図ることができる。
接触角αは、３５°〜５５°の範囲とすることでモーメント剛性を向上することができる。一対の円錐ころ軸受１を軸方向に配置し、それらの軸受間距離が短い場合、具体的には、軸受間距離が軸受の組立幅Ｔの４倍以下の場合に、接触角αを３５°〜５５°の範囲とすると、軸受のモーメント剛性を向上する上で特に有効である。 In the tapered roller bearing 1 of the present embodiment, the contact angle α, which is the angle formed between the tangent line of the outer ring raceway surface 2a and the rotational axis of the tapered roller 1, is set to 45 °. As a result, the moment stiffness can be improved, the roller length can be increased to increase the load capacity, and the high moment stiffness and longer life can be achieved.
The moment rigidity can be improved by setting the contact angle α to a range of 35 ° to 55 °. When the pair of tapered roller bearings 1 are arranged in the axial direction and the distance between the bearings is short, specifically, when the distance between the bearings is not more than four times the assembly width T of the bearing, the contact angle α is set to 35 °. A range of ˜55 ° is particularly effective in improving the moment rigidity of the bearing.

また、本実施形態に適用される円錐ころ軸受１としては、通常、軸受内径が３０〜５００ｍｍ、軸受外径が３３〜６５０ｍｍのものである。このサイズの軸受は、減速機に好適に使用することができる。したがって、減速機に使う場合、軸受サイズが風力発電機主軸用のものに比べて小さいため、円錐ころのサイズも小さく、重量も軽い。このため、円錐ころ軸受１には、本発明のような一体型の樹脂製保持器１０を採用している。   Moreover, as the tapered roller bearing 1 applied to this embodiment, the bearing inner diameter is usually 30 to 500 mm, and the bearing outer diameter is 33 to 650 mm. This size bearing can be suitably used for a reduction gear. Therefore, when used in a reduction gear, the bearing size is smaller than that for the main shaft of the wind power generator, so that the size of the tapered roller is small and the weight is light. Therefore, the tapered roller bearing 1 employs an integrated resin cage 10 as in the present invention.

図１〜図４に示すように、樹脂製保持器１０は、軸方向に離間した大径リング部１１及び小径リング部１２と、大径リング部１１及び小径リング部１２との間を繋ぐ、円周方向に所定の間隔で設けられた複数の柱部１３と、備える。柱部１３は、転動体である円錐ころ４の外周面に摺接する。樹脂製保持器１０は、円錐ころ４，４，・・・を収容保持するための複数のポケットＰ，Ｐ，・・・が周方向等分に形成される。   As shown in FIGS. 1 to 4, the resin cage 10 connects between the large-diameter ring portion 11 and the small-diameter ring portion 12 that are spaced apart in the axial direction, and the large-diameter ring portion 11 and the small-diameter ring portion 12. And a plurality of pillars 13 provided at predetermined intervals in the circumferential direction. The column portion 13 is in sliding contact with the outer peripheral surface of the tapered roller 4 that is a rolling element. In the resin cage 10, a plurality of pockets P, P,... For receiving and holding the tapered rollers 4, 4,.

保持器１０に使用可能な樹脂組成物に用いられるベース樹脂としては、一定以上の耐熱性を有する熱可塑性樹脂を使用することができる。
また、保持器１０として要求される耐疲労性と、低い吸水寸法変化を満足するために、結晶性樹脂の方が好適であり、具体的には、ポリアミド４６、ポリアミド６６、芳香族ポリアミド樹脂、ポリフェニレンサルファイド（ＰＰＳ）樹脂、ポリエーテルエーテルケトン（ＰＥＥＫ）樹脂等である。芳香族ポリアミド樹脂としては、ポリアミド６Ｔ／６Ｉ等の変性ポリアミド６Ｔ，ポリアミドＭＸＤ６，ポリアミド９Ｔ，ポリアミド４Ｔを使用することができる。以上説明したベース樹脂の中で、吸水寸法変化がほとんど無いポリフェニレンサルファイド（ＰＰＳ）樹脂、ポリエーテルエーテルケトン（ＰＥＥＫ）樹脂が特に好適である。 As the base resin used in the resin composition that can be used for the cage 10, a thermoplastic resin having a certain level of heat resistance can be used.
Further, in order to satisfy the fatigue resistance required for the cage 10 and a low water absorption dimensional change, a crystalline resin is more preferable. Specifically, polyamide 46, polyamide 66, aromatic polyamide resin, Polyphenylene sulfide (PPS) resin, polyether ether ketone (PEEK) resin, and the like. As the aromatic polyamide resin, modified polyamide 6T such as polyamide 6T / 6I, polyamide MXD6, polyamide 9T, and polyamide 4T can be used. Among the base resins described above, polyphenylene sulfide (PPS) resin and polyether ether ketone (PEEK) resin that hardly change in water absorption dimension are particularly suitable.

また、この樹脂組成物は、一定以上の強度を達成し、線膨張係数・吸水寸法変化を抑制するために、強化繊維材を含有する。強化繊維材としては、ガラス繊維、炭素繊維、アラミド繊維等の表面処理品（シランカップリング剤・サイジング剤で表面処理されることで、ベース樹脂との接着性向上）を好適に使用することができる。
樹脂組成物中の強化繊維材の含有量は、樹脂組成物全体の１０重量％以上４０重量％以下、より好ましくは１５〜３０重量％である。 Moreover, this resin composition contains a reinforcing fiber material in order to achieve a certain level of strength and to suppress changes in linear expansion coefficient and water absorption dimension. As the reinforcing fiber material, it is preferable to use a surface treatment product such as glass fiber, carbon fiber, and aramid fiber (adhesion with the base resin is improved by surface treatment with a silane coupling agent / sizing agent). it can.
Content of the reinforced fiber material in a resin composition is 10 to 40 weight% of the whole resin composition, More preferably, it is 15 to 30 weight%.

樹脂製保持器１０は、射出成形で製作されており、本実施形態では、コスト面で有利なアキシャルドロー型により射出成形されることが好ましい。   The resin cage 10 is manufactured by injection molding. In the present embodiment, the resin cage 10 is preferably injection molded by an axial draw mold that is advantageous in terms of cost.

また、柱部１３は、大径リング部寄りの部分と小径リング部寄りの部分において断面形状が異なっており、柱部１３の途中で切り替わっている。即ち、図４（ａ）に示す柱部１３の大径リング部寄りの部分は、円錐ころ４のピッチ円Ｃに対して内径側に円錐面１４ａが設けられた突出部１４を有している。また、図４（ｂ）に示す柱部１３の小径リング部寄りの部分は、円錐ころ４のピッチ円Ｃに対して外径側に円錐面１５ａが設けられた突出部１５を有している。
なお、円錐面１４ａ、１５ａの曲率は、円錐ころ４の曲率よりも若干大きく設定されている。 Moreover, the cross-sectional shape of the column portion 13 is different between the portion near the large-diameter ring portion and the portion near the small-diameter ring portion, and is switched in the middle of the column portion 13. That is, the portion near the large-diameter ring portion of the column portion 13 shown in FIG. 4A has a protruding portion 14 provided with a conical surface 14 a on the inner diameter side with respect to the pitch circle C of the tapered roller 4. . 4B has a protruding portion 15 having a conical surface 15a provided on the outer diameter side with respect to the pitch circle C of the tapered roller 4. .
The curvatures of the conical surfaces 14 a and 15 a are set slightly larger than the curvature of the tapered rollers 4.

また、円錐ころ４と樹脂製保持器１０とを一体にするため、柱部１３の大径リング部寄りの突出部１４では、ポケットの内径側開口幅Ｗ１は、ころ大径Ｄｗ１より狭く、柱部１３の小径リング部寄りの突出部１５では、ポケットの外径側開口幅Ｗ２は、ころ小径Ｄｗ２より狭い寸法となる。   Further, in order to integrate the tapered roller 4 and the resin cage 10, in the protruding portion 14 near the large diameter ring portion of the column portion 13, the pocket inner diameter side opening width W <b> 1 is narrower than the roller large diameter Dw <b> 1. In the protruding portion 15 of the portion 13 near the small-diameter ring portion, the outer diameter side opening width W2 of the pocket is smaller than the small roller diameter Dw2.

表１は、柱部１３の大径リング部寄りの突出部１４でのかかり代（Ｄｗ１−Ｗ１）を０．２〜０．７ｍｍの間で０．１ｍｍずつ変えて、柱部１３の小径リング部寄りの突出部１５でのかかり代（Ｄｗ２−Ｗ２）を０．１ｍｍ〜０．５ｍｍの間で０．１ｍｍずつ変えて、ころ挿入性及びころ保持性を試験した結果を示している。なお、その他の条件については、同一としている。また、ころ挿入性及びころ保持性の両方が良好である場合は◎とし、ころ挿入性及びころ保持性のいずれかが◎の場合よりも低いが実施可能である場合は○とし、ころ挿入性及びころ保持性のいずれかが実施不可能である場合は×とする。 Table 1 shows that the allowance (Dw1-W1) of the protruding portion 14 near the large-diameter ring portion of the column portion 13 is changed by 0.1 mm between 0.2 to 0.7 mm , and the small-diameter ring of the column portion 13 The result of testing the roller insertion property and the roller holding property by changing the allowance (Dw2-W2) at the protruding portion 15 closer to the portion by 0.1 mm between 0.1 mm and 0.5 mm. Other conditions are the same. Further, when both retention this filtrate insertional and rollers is good and ◎, is lower than either of the rollers insertional and roller retaining properties of ◎ is susceptible implementation and ○, this filtrate When either insertability or roller retainability is not feasible, it is marked as x .

この結果から、柱部１３の大径リング部寄りの突出部１４でのかかり代（Ｄｗ１−Ｗ１）を０．２ｍｍ〜０．７ｍｍとし、柱部１３の小径リング部寄りの突出部１５でのかかり代（Ｄｗ２−Ｗ２）を０．１ｍｍ〜０．５ｍｍとすることが好ましいことがわかる。特に、ころ挿入性ところ保持性との良好なバランスの観点から、柱部１３の大径リング部寄りの突出部１４でのかかり代（Ｄｗ１−Ｗ１）を０．２ｍｍ〜０．５ｍｍとし、柱部１３の小径リング部寄りの突出部１５でのかかり代（Ｄｗ２−Ｗ２）を０．１ｍｍ〜０．３ｍｍとすることが好ましい。 From this result, the margin (Dw1-W1) at the protrusion 14 near the large-diameter ring portion of the column portion 13 is set to 0.2 mm to 0.7 mm, and the protrusion 15 near the small-diameter ring portion of the column portion 13 It can be seen that it is preferable to set the allowance (Dw2-W2) of 0.1 mm to 0.5 mm. In particular, from the viewpoint of a good balance between the roller insertion property and the retaining property, the margin (Dw1-W1) at the protruding portion 14 near the large-diameter ring portion of the column portion 13 is set to 0.2 mm to 0.5 mm, It is preferable that the allowance (Dw2-W2) at the protruding portion 15 near the small-diameter ring portion of the column portion 13 is 0.1 mm to 0.3 mm.

Figure 0006432178
Figure 0006432178

また、図１及び図２に示すように、保持器１０の外周面及び内周面は互いに平行に形成されており、円錐ころ軸受１の回転軸線に対する保持器１０の外周面及び内周面の傾斜角度θ１は、円錐ころ軸受１の接触角αに対応して、３２°３０´以上５５°以下に設定される。 Further, as shown in FIGS. 1 and 2, the outer peripheral surface and the inner peripheral surface of the cage 10 are formed in parallel with each other, and the outer peripheral surface and the inner peripheral surface of the cage 10 with respect to the rotation axis of the tapered roller bearing 1. The inclination angle θ 1 is set to 32 ° 30 ′ or more and 55 ° or less corresponding to the contact angle α of the tapered roller bearing 1.

さらに、図２〜図４に示すように、大径リング部１１の内周面には、大径リング部１１の肉厚ｔ１が柱部１３の肉厚ｔよりも薄くなるように環状の切欠き部１６が形成され、保持器１０の内周面は、柱部１３から大径リング部１１にかけて段付き形状に形成される。また、切欠き部１６は、柱部１３の一部を径方向に沿って切欠いている。これにより、大径リング部１１の肉厚が薄くなるとともに、柱部１３の突出部１４も一部切除されるので、大径リング部側の柱部１３の弾性変形量が大きくなり、保持器１０の内側から円錐ころ４が挿入しやすくなる。 Furthermore, as shown in FIGS. 2 to 4, the inner circumferential surface of the large-diameter ring portion 11 has an annular shape so that the wall thickness t 1 of the large-diameter ring portion 11 is thinner than the wall thickness t of the column portion 13. A notch portion 16 is formed, and the inner peripheral surface of the cage 10 is formed in a stepped shape from the column portion 13 to the large-diameter ring portion 11. Moreover, the notch part 16 has notched a part of pillar part 13 along radial direction. As a result, the thickness of the large-diameter ring portion 11 is reduced, and the protruding portion 14 of the column portion 13 is partially cut away, so that the amount of elastic deformation of the column portion 13 on the large-diameter ring portion side is increased, and the cage It becomes easy to insert the tapered roller 4 from the inside of 10.

具体的に、図２に示すように、切欠き部１６は、大径リング部１１の軸方向端面から延びる第１の面１７、保持器１０の内周面から延びる第２の面１８、及び第１及び第２の面１７、１８を接続する第３の面１９によって構成される。   Specifically, as shown in FIG. 2, the notch portion 16 includes a first surface 17 extending from the axial end surface of the large diameter ring portion 11, a second surface 18 extending from the inner peripheral surface of the cage 10, and It is constituted by a third surface 19 connecting the first and second surfaces 17, 18.

また、保持器の内周面の延長線に対する第２の面１８の傾斜角度θ２は、（９０°−θ１）≦θ２≦９０°を満たすように設定することが好ましい。即ち、（９０°−θ１）≦θ２とするのは、内輪大鍔との接触を回避するためである。また、θ２≦９０°とするのは、切欠き部１６での強度を確保するためである。本実施形態では、内輪大鍔と干渉しない保持器を設計することを前提としており、θ２の上下限値を検討すると、θ２＞９０°となると、切欠き部１６での強度が不足となる虞があり、また、θ２＜９０°−θ１となると、内輪大鍔と接触する虞がある。
なお、本実施形態では、θ１＋θ２＝９０°、即ち、θ２を下限値とし、第２の面１８を半径方向に沿って延伸させている。これにより、大鍔３ｂの干渉を回避できるとともに、保持器１０の切欠き部１６の肉厚を極力大きくする設計となっているので、保持器１０の強度も確保することができる。 In addition, the inclination angle θ 2 of the second surface 18 with respect to the extension line of the inner peripheral surface of the cage is preferably set so as to satisfy (90 ° −θ 1 ) ≦ θ 2 ≦ 90 °. That is, (90 ° −θ 1 ) ≦ θ 2 is set to avoid contact with the inner ring collar. The reason why θ 2 ≦ 90 ° is to ensure the strength at the notch 16. In this embodiment, it is assumed that a cage that does not interfere with the inner ring collar is designed. When the upper and lower limit values of θ 2 are examined, if θ 2 > 90 °, the strength at the notch portion 16 is insufficient. In addition, when θ 2 <90 ° −θ 1 , there is a risk of contact with the inner ring large collar.
In the present embodiment, θ 1 + θ 2 = 90 °, that is, θ 2 is the lower limit value, and the second surface 18 is extended along the radial direction. Thereby, while being able to avoid interference of the large cage 3b, since the thickness of the notch part 16 of the holder | retainer 10 is designed as much as possible, the intensity | strength of the holder | retainer 10 can also be ensured.

さらに、大径リング部１１は、外周面及び内周面がそれぞれ軸方向へ延伸する円筒状端部２０を構成している。すなわち、端部２０を軸方向へ円筒状に延伸することで、図１に示す保持器１０は、外輪２との間に所定のすきまｇを確保することができると共に、図５の参考例に示す保持器１０´と比べて、保持器大径側の強度を向上することもできる。   Furthermore, the large-diameter ring portion 11 constitutes a cylindrical end portion 20 in which the outer peripheral surface and the inner peripheral surface each extend in the axial direction. That is, by extending the end portion 20 in the axial direction in a cylindrical shape, the cage 10 shown in FIG. 1 can secure a predetermined gap g between the outer ring 2 and the reference example of FIG. Compared with the cage 10 'shown, the strength on the cage larger diameter side can also be improved.

また、柱部１３の肉厚ｔは、円錐ころ４のころ平均径［（Ｄｗ１＋Ｄｗ２）／２］の３０〜７０％に設定され、大径リング部１１の肉厚ｔ１は、柱部１３の肉厚ｔの４０〜８０％に設定されている。 Further, the thickness t of the pillar portion 13 is set to 30% to 70% of the average tapered rollers 4 of the roller diameter [(Dw1 + Dw2) / 2 ], the thickness t 1 of the large-diameter ring portion 11, column portions 13 It is set to 40 to 80% of the wall thickness t.

大径リング部１１の肉厚ｔ１は、柱部１３の肉厚ｔの４０％未満であると、その厚さが薄くなり、強度低下の恐れがある。一方、大径リング部１１の肉厚ｔ１は、柱部１３の肉厚ｔの８０％超であると、円錐ころ４の挿入性が悪くなる虞があるほか、場合によっては、図１に示す大鍔３ｂと接触する可能性がある。 If the wall thickness t 1 of the large-diameter ring portion 11 is less than 40% of the wall thickness t of the column portion 13, the thickness becomes thin and the strength may be reduced. On the other hand, the thickness t 1 of the large-diameter ring portion 11, when is 80% of the thickness t of the pillar part 13, in addition there is a possibility that the insertion of the tapered roller 4 is deteriorated, in some cases, in FIG. 1 There is a possibility of contact with the large spear 3b shown.

なお、本実施形態の円錐ころ軸受１は、高モーメント剛性を得るためには、軸受配列として背面組合せ（ＤＢ組合せ）で使用することが望ましい。
また、円錐ころ軸受１は、予圧荷重を高めればモーメント剛性を向上する事が可能であるが、その反面、軸受の寿命が低下する可能性があるため、特殊熱処理(浸炭処理又は浸炭窒化処理)を施した長寿命鋼を使用することが好ましい。 In order to obtain high moment rigidity, it is desirable that the tapered roller bearing 1 of the present embodiment is used in a back surface combination (DB combination) as a bearing arrangement.
Further, the tapered roller bearing 1 can improve the moment rigidity if the preload is increased, but on the other hand, since the life of the bearing may be reduced, a special heat treatment (carburizing treatment or carbonitriding treatment) is performed. It is preferable to use long-life steel subjected to.

以上説明したように、本実施形態の円錐ころ軸受１によれば、内輪３には、大径側端部と小径側端部のうち、該大径側端部にのみ鍔部３ｂが形成されるので、ころ長さを最大限長くすることが可能となり、負荷容量を大きくとることができ、高モーメント剛性および長寿命化を図ることができる。また、円錐ころ軸受１の接触角αが３５°〜５５°であるので、モーメント剛性をさらに向上することができる。特に、軸受間距離が短い、具体的には、軸受間距離が軸受の組立幅Ｔの４倍以下の場合に、作用点間距離を長くすることができ、軸受のモーメント剛性を向上する上で有効である。
また、樹脂製保持器１０の大径リング部１１は、外周面及び内周面がそれぞれ軸方向へ延伸する円筒状端部２０を有するので、大径リング部１１の端部が外輪２及び内輪３と干渉するのを防止することができ、保持器大径側の強度を向上することもできる。 As described above, according to the tapered roller bearing 1 of the present embodiment, the inner ring 3 is formed with the flange portion 3b only at the large diameter side end portion of the large diameter side end portion and the small diameter side end portion. Therefore, the roller length can be maximized, the load capacity can be increased, and the high moment rigidity and the life can be increased. Further, since the contact angle α of the tapered roller bearing 1 is 35 ° to 55 °, the moment rigidity can be further improved. In particular, when the distance between the bearings is short, specifically, when the distance between the bearings is not more than 4 times the assembly width T of the bearing, the distance between the operating points can be increased, and the moment rigidity of the bearing is improved. It is valid.
Moreover, since the large diameter ring part 11 of the resin cage 10 has a cylindrical end part 20 in which the outer peripheral surface and the inner peripheral surface respectively extend in the axial direction, the end part of the large diameter ring part 11 is the outer ring 2 and the inner ring. 3 can be prevented, and the strength on the large diameter side of the cage can be improved.

さらに、柱部１３は、大径リング部寄りの突出部１４において、０．２ｍｍ〜０．７ｍｍのかかり代とし、ポケットＰの内径側開口幅Ｗ１が円錐ころ４のころ大径Ｄｗ１より狭くなるように形成され、且つ、小径リング部寄りの突出部１５において、０．１ｍｍ〜０．５ｍｍのかかり代とし、ポケットＰの外径側開口幅Ｗ２が円錐ころ４のころ小径Ｄｗ２より狭くなるように形成される。このように、保持器１０のかかり代を設定することで、保持器１０のころ保持性能を向上させ、円錐ころ４と保持器１０の一体化を実現している。よって、本実施形態の円錐ころ軸受１に採用される保持器１０は、本来円錐ころ４を保持する機能を果たす内輪小鍔の代わりにその役割を担うことを実現しており、接触角が３５°〜５５°の急勾配円錐ころ軸受１のころ落下を有効的に抑制することができる。
即ち、柱部１３は、ポケットＰの内径側の少なくとも一部において、０．２ｍｍ〜０．７ｍｍのかかり代とし、ポケットＰの内径側開口幅Ｗ１が円錐ころ４のころ大径Ｄｗ１より狭くなるように形成され、且つ、ポケットＰの外径側の少なくとも一部において、０．１ｍｍ〜０．５ｍｍのかかり代とし、ポケットＰの外径側開口幅Ｗ２が円錐ころ４のころ小径Ｄｗ２より狭くなるように形成されればよい。 Further, the pillar portion 13 has a margin of 0.2 mm to 0.7 mm in the protruding portion 14 near the large diameter ring portion, and the inner diameter side opening width W1 of the pocket P is narrower than the large roller diameter Dw1 of the tapered roller 4. It is formed such that, and, at the projecting portions 15 of the small-diameter ring portion closer to the engagement allowance of 0.1 mm to 0.5 mm, the outer diameter side opening width W2 of the pocket P is smaller than the roller diameter Dw2 of the tapered roller 4 Formed to be. Thus, the roller holding performance of the retainer 10 is improved by setting the allowance for the retainer 10, and the tapered roller 4 and the retainer 10 are integrated. Therefore, the cage 10 employed in the tapered roller bearing 1 of the present embodiment realizes its role in place of the inner ring gavel that originally functions to hold the tapered roller 4, and has a contact angle of 35. The roller fall of the steep tapered roller bearing 1 of ˜55 ° can be effectively suppressed.
That is, the column portion 13 has a margin of 0.2 mm to 0.7 mm in at least part of the inner diameter side of the pocket P, and the inner diameter side opening width W1 of the pocket P is narrower than the roller large diameter Dw1 of the tapered roller 4. The outer diameter side opening width W2 of the pocket P is a small roller diameter Dw2 of the tapered roller 4 with a margin of 0.1 mm to 0.5 mm in at least a part of the outer diameter side of the pocket P. What is necessary is just to form so that it may become narrower.

また、大径リング部１１の内周面には、該リング部１１の肉厚ｔ１が柱部１３の肉厚ｔよりも薄くなるように、第１の面１７、第２の面１８、及び第１及び第２の面１７、１８を接続する第３の面１９によって構成される切欠き部１６が設けられるので、大鍔３ｂとの接触を回避しつつ、且つ、切欠き部１６の強度を確保することができる。 The inner circumferential surface of the large-diameter ring portion 11, as the thickness t 1 of the ring portion 11 is thinner than the thickness t of the pillar portion 13, the first surface 17, second surface 18, And the notch 16 formed by the third surface 19 connecting the first and second surfaces 17 and 18 is provided, so that contact with the large collar 3b is avoided and the notch 16 Strength can be secured.

また、大径リング部１１の肉厚ｔ１が柱部１３の肉厚ｔの４０〜８０％であり、且つ、柱部１３の肉厚ｔが円錐ころ４のころ平均径［（Ｄｗ１＋Ｄｗ２）／２］の３０〜７０％であるので、大径リング部１１の強度を確保することができ、且つ、円錐ころ４の挿入性を確保しつつ、大鍔３ｂとの接触を回避することができる。 Further, the wall thickness t 1 of the large-diameter ring portion 11 is 40 to 80% of the wall thickness t of the column portion 13, and the wall thickness t of the column portion 13 is the average roller diameter of the tapered roller 4 [(Dw1 + Dw2) / 2] is 30 to 70%, the strength of the large-diameter ring portion 11 can be ensured, and the insertion of the tapered roller 4 can be ensured while the contact with the large collar 3b can be avoided. .

また、保持器１０の傾斜角度θ１は、３２°３０´以上５５°以下に設定されるので、保持器１０は、接触角αが３５°〜５５°の急勾配の円錐ころ軸受１にも適用することができる。 In addition, since the inclination angle θ 1 of the cage 10 is set to 32 ° 30 ′ or more and 55 ° or less, the cage 10 is also applied to the steep tapered roller bearing 1 having a contact angle α of 35 ° to 55 °. Can be applied.

また、外輪２の大径側端部と内輪３の小径側端部には、軸方向に延びる軸方向延長部２ｂ、３ｃが形成されるので、軸受を装置へ組付ける際の取付け性を向上することができると共に、良好な位置決め性が得られ、さらに、軌道輪の軸方向長さを延長することができるため、軸やハウジングへの組込み性を向上することができる。   Further, since the axial extension portions 2b and 3c extending in the axial direction are formed at the large-diameter side end portion of the outer ring 2 and the small-diameter side end portion of the inner ring 3, the mounting property when the bearing is assembled to the apparatus is improved. In addition, it is possible to obtain a good positioning property and to extend the axial length of the raceway, so that it is possible to improve the assemblability into the shaft and the housing.

なお、本発明の切欠き部１６は、２つ以上の面によって構成されるものであればよく、切欠き部１６の強度が十分確保できるものであれば、例えば、図６に示す変形例のように、軸方向へ延伸する第１の面１７と径方向に延伸する第２の面１８とを直接接続するようにしてもよい。   In addition, the notch part 16 of this invention should just be comprised by two or more surfaces, and if the intensity | strength of the notch part 16 can fully ensure, for example, the modification shown in FIG. As described above, the first surface 17 extending in the axial direction and the second surface 18 extending in the radial direction may be directly connected.

（第２実施形態）
次に、本発明の第２実施形態に係る円錐ころ軸受について、図面に基づき詳細に説明する。
上記実施形態では、外輪２の大径側端部と内輪３の小径側端部に、軸方向に延びる軸方向延長部２ｂ、３ｃが形成されていたが、図７に示す本実施形態のように、外輪２の大径側端部と内輪３の小径側端部は、軸方向延長部を有しない構成であってもよい。
なお、本実施形態では、その他の構成及び作用については、第１実施形態と同様であり、第１実施形態と同一の樹脂製保持器が使用されている。つまり、樹脂製保持器に関して、そのかかり代、切欠き部、形状、傾斜角度等の設計は、第１実施形態と同様であるので、説明を省略している。
また、本発明の軸方向延長部は、外輪の大径側端部と前記内輪の小径側端部の少なくとも一方に形成される構成であってもよい。 (Second Embodiment)
Next, a tapered roller bearing according to a second embodiment of the present invention will be described in detail with reference to the drawings.
In the above embodiment, the axial extension portions 2b and 3c extending in the axial direction are formed at the large diameter side end portion of the outer ring 2 and the small diameter side end portion of the inner ring 3, but as in the present embodiment shown in FIG. Moreover, the structure which does not have an axial direction extension part may be sufficient as the large diameter side edge part of the outer ring | wheel 2, and the small diameter side edge part of the inner ring | wheel 3.
In addition, in this embodiment, about another structure and effect | action, it is the same as that of 1st Embodiment, and the resin-made cage same as 1st Embodiment is used. That is, regarding the resin cage, its design, such as the allowance, the notch, the shape, and the inclination angle, is the same as in the first embodiment, and thus the description thereof is omitted.
The axial extension of the present invention may be formed on at least one of a large-diameter side end of the outer ring and a small-diameter side end of the inner ring.

（第３実施形態）
次に、本発明の第３実施形態に係る円錐ころ軸受について、図面に基づき詳細に説明する。
上記実施形態では、図８に示すように、外輪２の大径側端部と内輪３の小径側端部に形成される軸方向延長部２ｂ、３ｃを軸方向にさらに伸ばして、外輪２及び内輪３の軸方向長さが組立幅と同じ長さになるように設定されている。
したがって、本実施形態においても、第１実施形態と同一の樹脂製保持器が使用されることで、軸方向延長部２ｂ、３ｃが長い外輪２及び内輪３と干渉するのを防止することができる。つまり、樹脂製保持器に関して、そのかかり代、切欠き部、形状、傾斜角度等の設計は、第１実施形態と同様であるので、説明を省略している。 (Third embodiment)
Next, a tapered roller bearing according to a third embodiment of the present invention will be described in detail with reference to the drawings.
In the above embodiment, as shown in FIG. 8, the axial extension portions 2 b and 3 c formed at the large-diameter side end portion of the outer ring 2 and the small-diameter side end portion of the inner ring 3 are further extended in the axial direction. The axial length of the inner ring 3 is set to be the same as the assembly width.
Therefore, also in this embodiment, the same resin cage as that in the first embodiment is used, so that the axially extending portions 2b and 3c can be prevented from interfering with the long outer ring 2 and inner ring 3. . That is, regarding the resin cage, its design, such as the allowance, the notch, the shape, and the inclination angle, is the same as in the first embodiment, and thus the description thereof is omitted.

なお、本発明は、上述した実施形態に限定されるものでなく、適宜、変形、改良などが可能である。   In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

１ 円錐ころ軸受
２ 外輪
２ａ 外輪軌道面
２ｂ、３ｃ 軸方向延長部
３ 内輪
３ａ 内輪軌道面
３ｂ 大鍔（鍔部）
４ 円錐ころ
４ａ 大径側端面
１０ 円錐ころ軸受用樹脂製保持器
１１ 大径リング部
１２ 小径リング部
１３ 柱部
１４、１５ 突出部
１６ 切欠き部
１７ 第１の面
１８ 第２の面
１９ 第３の面
２０ 円筒状端部（端部）
Ｐ ポケット
α 接触角
θ１ 保持器傾斜角度
θ２ 柱部の内周面と切欠き部の第２の面とのなす角度 DESCRIPTION OF SYMBOLS 1 Tapered roller bearing 2 Outer ring 2a Outer ring raceway surface 2b, 3c Axial extension part 3 Inner ring 3a Inner ring raceway surface 3b
4 Tapered roller 4a Large-diameter end face 10 Resin cage for tapered roller bearing 11 Large-diameter ring portion 12 Small-diameter ring portion 13 Column portions 14, 15 Protruding portion 16 Notch portion 17 First surface 18 Second surface 19 First 3 side 20 cylindrical end (end)
P Pocket α Contact angle θ 1 Cage inclination angle θ 2 Angle formed between the inner peripheral surface of the pillar and the second surface of the notch

Claims (6)

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円錐ころと、
軸方向に離間した大径リング部及び小径リング部と、該大径リング部及び小径リング部との間を繋ぐ複数の柱部と、を有し、前記円錐ころを収容保持する複数のポケットを画成する樹脂製保持器と、
を備える円錐ころ軸受において、
前記円錐ころ軸受の接触角αが３５°〜５５°であり、
前記内輪は、大径側端部と小径側端部のうち、大径側端部にのみ鍔部が形成され、且つ、
前記樹脂製保持器の大径リング部は、軸方向へ延伸する端部を有し、
前記大径リング部の内周面には、該リング部の肉厚が前記柱部の肉厚よりも薄くなるように、切欠き部が設けられ、
前記切欠き部は、前記柱部における、前記円錐ころの転走面と対向する部分から前記大径リング部にかけて、前記柱部の一部を切欠いて形成されることを特徴とする円錐ころ軸受。 An outer ring having an outer ring raceway surface on the inner circumferential surface;
An inner ring having an inner ring raceway surface on the outer peripheral surface;
A plurality of tapered rollers disposed between the outer ring raceway surface and the inner ring raceway surface in a freely rollable manner;
A plurality of pockets for accommodating and holding the tapered rollers, and a large-diameter ring portion and a small-diameter ring portion that are spaced apart in the axial direction, and a plurality of pillar portions that connect the large-diameter ring portion and the small-diameter ring portion. A resin cage to define,
In a tapered roller bearing comprising:
The tapered roller bearing has a contact angle α of 35 ° to 55 °,
The inner ring has a flange formed only at the large-diameter end among the large-diameter end and the small-diameter end, and
The large-diameter ring portion of the resin cage can have a end which extends in the axial direction,
A cutout portion is provided on the inner peripheral surface of the large-diameter ring portion so that the thickness of the ring portion is thinner than the thickness of the column portion,
The notch is in the pillar portion, said from rolling surface opposed to part of the tapered roller toward the large diameter ring portion, tapered roller bearing, characterized in Rukoto formed by notching a portion of the pillar portion . 前記柱部は、前記ポケットの内径側の少なくとも一部において、０．２ｍｍ〜０．７ｍｍのかかり代とし、前記ポケットの内径側開口幅が前記円錐ころのころ大径より狭くなるように形成され、且つ、前記ポケットの外径側の少なくとも一部において、０．１ｍｍ〜０．５ｍｍのかかり代とし、前記ポケットの外径側開口幅が前記円錐ころのころ小径より狭くなるように形成されることを特徴とする請求項１に記載の円錐ころ軸受。   The column portion is formed with a margin of 0.2 mm to 0.7 mm in at least a part of the inner diameter side of the pocket, and the inner diameter side opening width of the pocket is narrower than the large diameter of the tapered roller. In addition, at least part of the outer diameter side of the pocket is formed with a margin of 0.1 mm to 0.5 mm, and the outer diameter side opening width of the pocket is narrower than the small roller diameter of the tapered roller. The tapered roller bearing according to claim 1. 前記切欠き部は、前記大径リング部の肉厚が前記柱部の肉厚よりも薄くなるように、第１の面、第２の面、及び第１及び第２の面を接続する第３の面によって構成されることを特徴とする請求項１又は２に記載の円錐ころ軸受。 The notch portion connects the first surface, the second surface, and the first and second surfaces so that the thickness of the large-diameter ring portion is thinner than the thickness of the column portion. The tapered roller bearing according to claim 1 , wherein the tapered roller bearing is configured by three surfaces. 前記大径リング部の肉厚が前記柱部の肉厚の４０〜８０％であり、且つ、
前記柱部の肉厚が前記円錐ころのころ平均径の３０〜７０％であることを特徴とする請求項１〜３のいずれか１項に記載の円錐ころ軸受。 The wall thickness of the large-diameter ring part is 40 to 80% of the wall thickness of the column part, and
The tapered roller bearing according to any one of claims 1 to 3, wherein a thickness of the column portion is 30 to 70% of an average roller diameter of the tapered roller. 前記保持器の傾斜角度は、３２°３０´以上５５°以下に設定されることを特徴とする請求項１〜４のいずれか１項に記載の円錐ころ軸受。 The tapered roller bearing according to any one of claims 1 to 4 , wherein an inclination angle of the cage is set to 32 ° 30 'or more and 55 ° or less. 前記外輪の大径側端部と前記内輪の小径側端部の少なくとも一方には、軸方向に延びる軸方向延長部が形成されることを特徴とする請求項１〜５のいずれか１項に記載の円錐ころ軸受。 The axial extension part extended in an axial direction is formed in at least one of the large diameter side edge part of the said outer ring | wheel, and the small diameter side edge part of the said inner ring | wheel, The any one of Claims 1-5 characterized by the above-mentioned. The tapered roller bearing described.
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