WO2016194981A1 - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
WO2016194981A1
WO2016194981A1 PCT/JP2016/066290 JP2016066290W WO2016194981A1 WO 2016194981 A1 WO2016194981 A1 WO 2016194981A1 JP 2016066290 W JP2016066290 W JP 2016066290W WO 2016194981 A1 WO2016194981 A1 WO 2016194981A1
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WO
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Prior art keywords
diameter
small
inner ring
ring
diameter side
Prior art date
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PCT/JP2016/066290
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French (fr)
Japanese (ja)
Inventor
康由 林
貴司 脇坂
Original Assignee
Ntn株式会社
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Publication date
Priority claimed from JP2016067478A external-priority patent/JP6329198B2/en
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2016194981A1 publication Critical patent/WO2016194981A1/en

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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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication

Definitions

  • the present invention relates to a tapered roller bearing used in a reduction gear of a robot or a construction machine, particularly a taper used for an application requiring high load capacity, high rigidity and compactness under a condition where a high moment load is applied.
  • the present invention relates to a roller bearing.
  • Patent Document 1 Patent Document 1
  • Patent Document 2 Patent Document 1 are provided with a flange portion protruding in the direction, eliminating the small flange on the small diameter side end portion of the inner ring, and increasing the roller length by the amount of the small flange to increase the load capacity. It is disclosed in Document 3.
  • the tapered roller bearings of Patent Document 1 and Patent Document 2 are provided with a small-diameter side protruding portion that protrudes in the axial direction on the small-diameter side of the inner ring.
  • the tapered roller bearings of Patent Document 2 and Patent Document 3 have a steep gradient of contact angle of 35 ° to 55 ° so as to obtain high moment rigidity.
  • JP 2007-32679 A Japanese Unexamined Patent Publication No. 2016-8641 International Publication Number WO2014 / 104132
  • the tapered roller bearing 1 disclosed in Patent Document 2 or Patent Document 3 has a steep contact angle ⁇ of 35 ° to 55 °, and an outer ring raceway on an inner peripheral surface.
  • An outer ring 2 having a surface 2a, an inner ring 3 having an inner ring raceway surface 3a on the outer peripheral surface, and a plurality of tapered rollers 4 disposed so as to roll between the outer ring raceway surface 2a and the inner ring raceway surface 3a;
  • a cage 10 having a plurality of pockets P for accommodating and holding the plurality of tapered rollers 4 at a predetermined interval, and only the large-diameter side end of the inner ring 3 on the large-diameter side end and the small-diameter side end.
  • a flange portion 3b that protrudes radially outward is provided, the small flange on the small diameter side end portion of the inner ring 3 is eliminated, and the length of the tapered roller 4 is increased by the amount of the small flange to increase the load capacity.
  • the cage 10 accommodates and holds large-diameter ring portions 10a and small-diameter ring portions 10b that are separated in the axial direction, and tapered rollers 4 provided at predetermined intervals between the large-diameter ring portion 10a and the small-diameter ring portion 10b. And a column portion 10c that partitions a plurality of pockets P.
  • the width e of the column portion 10c of the cage 10 is narrowed, there is a limit in terms of manufacturing limit and strength of the cage 10 as well, and there is a limit in reducing the width of the cage 10 while the tapered roller bearing 1 is rotating.
  • the cage 10 comes into contact with the outer ring raceway surface 2a of the outer ring 2 and the inner ring raceway surface 3a of the inner ring 3, and the outer ring raceway surface 2a of the outer ring 2 and the inner ring 3
  • the inner raceway surface 3a may be scratched or worn, and abnormalities such as vibration may occur when the tapered roller 4 rolls.
  • Ratio of roller length Lw and inner ring width B is 0.8 ⁇ Lw / B ⁇ 1.2 2. 0.7 ⁇ (D1-d) / 2H ⁇ 0.9, where inner ring inner diameter d, inner ring outer diameter D1, and inner ring large collar side height is (D1-d) / 2. 3.
  • the ratio of the radial cross-sectional thickness H to the inner diameter d is 0.05 ⁇ H / d ⁇ 0.15 4).
  • the ratio of the roller large diameter Dw1 to the radial cross-sectional thickness H is 0.3 ⁇ Dw1 / H ⁇ 0.6
  • Patent Document 2 it is considered that providing a small-diameter-side protruding portion 11 that protrudes in the axial direction on the small-diameter side of the inner ring 3 is effective in preventing deformation of the fitting surface directly below the tapered roller 4.
  • Patent Document 2 does not disclose at all whether it is effective for the occurrence of creep if it is defined in the dimensional relationship.
  • the thickness of the inner ring 3 is increased, the compactness is inferior, and if the number of tapered rollers 4 is reduced, the load capacity is reduced.
  • the present invention prevents scratches or wear caused by the cage coming into contact with the outer ring raceway surface of the outer ring or the inner ring raceway surface of the inner ring so that the cage does not come into contact with the outer ring raceway surface of the outer ring or the inner ring raceway surface of the inner ring. It is an object of the present invention to provide a tapered roller bearing that can prevent the occurrence of creep and suppress the occurrence of creep due to deformation of the fitting surface directly below the tapered roller.
  • the present invention provides 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 an outer ring raceway surface between the outer ring raceway surface and the inner ring raceway surface.
  • the large-diameter end has a flange protruding outward in the radial direction only, and a small-diameter protrusion protruding in the axial direction is provided on the small-diameter side of the inner ring.
  • the inner ring raceway surface is positioned on the inner diameter side of the outer diameter side end portion of the inner ring raceway surface, the end surface of the small diameter side projecting portion projects to the smaller diameter side than the end surface on the smaller diameter side of the cage, and the contact angle is 35 ° or more.
  • the cage includes a large-diameter ring portion and a small diameter portion separated in the axial direction.
  • Both the gap between the outer diameter surface of the flange at the large-diameter side end of the inner ring and the gap between the inner peripheral surface of the small-diameter ring part and the outer diameter surface of the small-diameter side protrusion of the inner ring are pillars. It is smaller than the clearance gap between a part and the inner ring raceway surface of an inner ring.
  • a gap between the inner peripheral surface of the large-diameter ring portion and the outer-diameter surface of the flange on the large-diameter side end of the inner ring, and the outer peripheral surface of the inner peripheral surface of the small-diameter ring portion and the small-diameter side protrusion of the inner ring may be the same.
  • a grease retaining groove may be provided at the joint between the inner ring raceway surface of the inner ring and the small-diameter side protruding portion.
  • the cage does not contact the outer ring raceway surface of the outer ring or the inner ring raceway surface of the inner ring even when the amount of swirling of the cage during rotation of the tapered roller bearing increases. Can prevent the cage from coming into contact with the outer ring raceway surface and the inner ring raceway surface of the inner ring, and can also prevent the occurrence of creep due to deformation of the fitting surface directly below the tapered roller. .
  • the tapered roller bearing 11 according to the present invention has a steep contact angle ⁇ of 35 ° or more, and the tapered roller bearing 11 of the embodiment shown in FIGS. 1 and 2 has a contact angle ⁇ of 45 °.
  • the tapered roller bearing 11 includes an outer ring 12 having an outer ring raceway surface 12a on an inner peripheral surface, an inner ring 13 having an inner ring raceway surface 13a on an outer peripheral surface, and the outer ring raceway surface 12a and the inner ring raceway surface 13a.
  • a plurality of tapered rollers 14 disposed so as to be able to roll between, and a retainer 20 having a plurality of pockets P for accommodating and holding the plurality of tapered rollers 14 at a predetermined interval.
  • the portion and the small-diameter side end portion only the large-diameter side end portion has a flange portion 13b protruding outward in the radial direction.
  • a small-diameter protruding portion 13c protruding in the axial direction is provided at the small-diameter side end of the inner ring 13.
  • Outer diameter D 1 of the small diameter side protruding portion 13c is located on the inner diameter side than the outer diameter D 2 of the smaller diameter end of the inner ring raceway surface 13a of the inner ring 13, the end surface 13e of the small diameter side protruding portion 13c is held It protrudes to the smaller diameter side than the end surface 20d on the smaller diameter side of the vessel 20.
  • the outer diameter surface 13d of the small diameter side protruding portion 13c is formed in a plane parallel to the axis of the inner ring 13.
  • the cage 20 accommodates and holds large-diameter ring portions 20a and small-diameter ring portions 20b that are separated in the axial direction, and tapered rollers 14 that are provided between the large-diameter ring portion 20a and the small-diameter ring portion 20b at a predetermined interval. And a column portion 20c that partitions a plurality of pockets P.
  • a gap b between the inner peripheral surface of the ring portion 20a and the outer diameter surface of the flange portion 13b at the end on the large diameter side of the inner ring 13 is used to form the clearance 20b of the retainer 10 and the inner ring raceway surface 13a and outer ring 12 of the inner ring 13.
  • the cage 20 is made smaller than the gaps c and d between the outer ring raceway surface 12a and the retainer 10 before the column portion 20c of the cage 10 contacts the outer ring raceway surface 12a of the outer ring 12 and the inner ring raceway surface 13a of the inner ring 13. Both ends of 20 contact the outer diameter surface of the flange portion 13b at the large-diameter side end of the inner ring 13 and the outer diameter surface of the small-diameter protruding portion 13c of the inner ring 13, and the outer ring raceway surface 12a of the outer ring 12 is guided by this contact. Further, damage to the inner ring raceway surface 13a of the inner ring 13 is prevented.
  • the outer diameter surface of the small diameter side protruding portion 13c of the inner ring 13 and the outer diameter surface of the flange portion 13b of the large diameter side end portion of the inner ring 13 are parallel to the axial direction. It is desirable to make it.
  • both ends of the cage 20 can be supported with respect to the inner ring 13, so that the moment load applied to the cage 20 can be reduced as compared with the case where it is supported on one side. Can do.
  • a grease retaining groove 13f is formed at a joint portion between the inner ring raceway surface 13a of the inner ring 13 and the small diameter side protruding portion 13c.
  • the lubrication failure on the small diameter side of the inner ring raceway surface 13a of the inner ring 13 can be reduced by collecting the grease in the grease retaining groove 13f.
  • the grease retaining groove 13f is provided at the joint between the inner ring raceway surface 13a of the inner ring 13 and the small-diameter side protruding portion 13c, when the tapered roller bearing 11 is erected in the vertical direction, the small-diameter side thin portion of the tapered roller 14 is provided. Since the tapered roller 4 can be held by being caught in the grease retaining groove 13f, the grease retaining groove 13f functions as a small scissors that retains the tapered roller 4.
  • the inventor of the present invention relates to the relationship between the axial dimensions on the inner diameter surface of the inner ring 13, that is, the large flange axial dimension P, the axial dimension directly below the tapered roller 14 (Lw ⁇ cos ⁇ ), and the small-diameter side protrusion. It has been found that the occurrence of creep can be suppressed by defining the relationship of the axial dimension Q of the portion 13c as follows.

Abstract

The purpose of the present invention is to solve the problem of preventing damage and wear from occurring on both the outer ring raceway surface 12a of an outer ring 12 and the inner ring raceway surface 13a of an inner ring 13 even if the amount of runout of a retainer 20 increases, the damage and wear being caused by the contact of the retainer 20 with the outer ring raceway surface 12a and the inner ring raceway surface 13a. A tapered roller bearing 11 has a large contact angle of 35 degrees or greater. The retainer 20 is provided with: a large-diameter ring section 20a and a small-diameter ring section 20b, which are axially separated from each other; and column sections 20c provided at predetermined intervals between the large-diameter ring section 20a and the small-diameter ring section 20b and defining a plurality of pockets P for accommodating and retaining tapered rollers 14. The tapered roller bearing is characterized in that both the gap b between the inner peripheral surface of the large-diameter ring section 20a and the outer diameter surface of a flange section 13 at the large-diameter-side end of the inner ring 13, and the gap a between the inner peripheral surface of the small-diameter ring section 20b and the outer diameter surface of the small-diameter-side protrusion 13c of the inner ring 13 are smaller than the gap c between the inner ring raceway surface 13a of the inner ring 13 and the column sections 20c.

Description

円すいころ軸受Tapered roller bearing
　この発明は、ロボットや建設機械の減速機で使用される円すいころ軸受、特に、高いモーメント荷重が負荷される条件の下、高負荷容量、高剛性且つコンパクト性が求められる用途に使用される円すいころ軸受に関する。 The present invention relates to a tapered roller bearing used in a reduction gear of a robot or a construction machine, particularly a taper used for an application requiring high load capacity, high rigidity and compactness under a condition where a high moment load is applied. The present invention relates to a roller bearing.
　この種の高負荷容量、高剛性且つコンパクト性が求められる用途に使用される円すいころ軸受として、内輪の大径側端部と小径側端部のうち、大径側端部にのみ半径方向外方に突出する鍔部を設け、内輪の小径側端部の小鍔をなくし、小鍔の分だけころ長さを長くして高負荷容量化したものが、特許文献１、特許文献２、特許文献３に開示されている。 Tapered roller bearings used in applications that require this type of high load capacity, high rigidity, and compactness. Out of the large diameter side end and the small diameter side end of the inner ring, only the large diameter side end is radially outward. Patent Document 1, Patent Document 2, Patent Document 1 are provided with a flange portion protruding in the direction, eliminating the small flange on the small diameter side end portion of the inner ring, and increasing the roller length by the amount of the small flange to increase the load capacity. It is disclosed in Document 3.
　特許文献１と特許文献２の円すいころ軸受は、内輪の小径側に軸方向に突出する小径側突出部を設けている。 The tapered roller bearings of Patent Document 1 and Patent Document 2 are provided with a small-diameter side protruding portion that protrudes in the axial direction on the small-diameter side of the inner ring.
　また、特許文献２と特許文献３の円すいころ軸受は、接触角を３５°～５５°という急こう配にして、高モーメント剛性を得るようにしている。 In addition, the tapered roller bearings of Patent Document 2 and Patent Document 3 have a steep gradient of contact angle of 35 ° to 55 ° so as to obtain high moment rigidity.
特開２００７－３２６７９号公報JP 2007-32679 A 特開２０１６－８６４１号公報Japanese Unexamined Patent Publication No. 2016-8641 国際公開番号ＷＯ２０１４／１０４１３２International Publication Number WO2014 / 104132
　特許文献２又は特許文献３に開示された円すいころ軸受１は、図４及び図５に示すように、接触角αが３５°～５５°という急勾配のものであり、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、前記外輪軌道面２ａと前記内輪軌道面３ａとの間に転動自在に配置される複数の円すいころ４と、この複数の円すいころ４を所定の間隔で収容保持する複数のポケットＰを有する保持器１０とを備え、内輪３の大径側端部と小径側端部のうち、大径側端部にのみ半径方向外方に突出する鍔部３ｂを設け、内輪３の小径側端部の小鍔をなくし、小鍔の分だけ円すいころ４の長さを長くして高負荷容量化を図っている。 As shown in FIGS. 4 and 5, the tapered roller bearing 1 disclosed in Patent Document 2 or Patent Document 3 has a steep contact angle α of 35 ° to 55 °, and an outer ring raceway on an inner peripheral surface. An outer ring 2 having a surface 2a, an inner ring 3 having an inner ring raceway surface 3a on the outer peripheral surface, and a plurality of tapered rollers 4 disposed so as to roll between the outer ring raceway surface 2a and the inner ring raceway surface 3a; A cage 10 having a plurality of pockets P for accommodating and holding the plurality of tapered rollers 4 at a predetermined interval, and only the large-diameter side end of the inner ring 3 on the large-diameter side end and the small-diameter side end. A flange portion 3b that protrudes radially outward is provided, the small flange on the small diameter side end portion of the inner ring 3 is eliminated, and the length of the tapered roller 4 is increased by the amount of the small flange to increase the load capacity.
　前記保持器１０は、軸方向に離れた大径リング部１０ａ及び小径リング部１０ｂと、大径リング部１０ａと小径リング部１０ｂとの間に所定の間隔で設けられた円すいころ４を収容保持する複数のポケットＰを区画する柱部１０ｃとを備えている。
　ところで、円すいころ軸受１のコンパクト性を考慮して、円すいころ軸受１の断面（寸法Ｈ及び寸法Ｔ）を小さくした場合、保持器１０の柱部１０ｃと外輪２の外輪軌道面２ａとの間の隙間ｄ、及び保持器１０の柱部１０ｃと内輪３の内輪軌道面３ａとの間の隙間ｃを確保するためには、保持器１０の柱部１０ｃの幅ｅを細くする必要がある。 The cage 10 accommodates and holds large-diameter ring portions 10a and small-diameter ring portions 10b that are separated in the axial direction, and tapered rollers 4 provided at predetermined intervals between the large-diameter ring portion 10a and the small-diameter ring portion 10b. And a column portion 10c that partitions a plurality of pockets P.
By the way, in consideration of the compactness of the tapered roller bearing 1, when the cross section (dimension H and dimension T) of the tapered roller bearing 1 is reduced, it is between the column portion 10c of the cage 10 and the outer ring raceway surface 2a of the outer ring 2. In order to secure the clearance d between the pillar 10c of the cage 10 and the inner raceway surface 3a of the inner ring 3, it is necessary to reduce the width e of the pillar 10c of the cage 10.
　しかしながら、保持器１０の柱部１０ｃの幅ｅを細くするにしても、保持器１０の製造限界、強度の点から細くするにも限界があり、円すいころ軸受１の回転中における保持器１０の振れまわり量が隙間ｄと隙間ｃよりも大きくなると、保持器１０が、外輪２の外輪軌道面２ａや内輪３の内輪軌道面３ａに接触して、外輪２の外輪軌道面２ａや内輪３の内輪軌道面３ａに傷や摩耗が生じ、円すいころ４の転がり時に振動などの異常が発生する恐れがある。 However, even if the width e of the column portion 10c of the cage 10 is narrowed, there is a limit in terms of manufacturing limit and strength of the cage 10 as well, and there is a limit in reducing the width of the cage 10 while the tapered roller bearing 1 is rotating. When the amount of swirling becomes larger than the clearances d and c, the cage 10 comes into contact with the outer ring raceway surface 2a of the outer ring 2 and the inner ring raceway surface 3a of the inner ring 3, and the outer ring raceway surface 2a of the outer ring 2 and the inner ring 3 The inner raceway surface 3a may be scratched or worn, and abnormalities such as vibration may occur when the tapered roller 4 rolls.
　また、特許文献３の接触角αが３５°～５５°という急勾配の円すいころ軸受１において、コンパクト性も考慮し、以下のような寸法規定を行っている。 Further, in the tapered roller bearing 1 having a steep slope with a contact angle α of 35 ° to 55 ° disclosed in Patent Document 3, the following dimensions are defined in consideration of compactness.
　１．ころ長さＬｗと内輪幅Ｂの比が０．８＜Ｌｗ/Ｂ＜１．２
　２．内輪内径ｄ、内輪外径Ｄ１とし、内輪大鍔側高さを（Ｄ１－ｄ）/２としたとき０．７＜（Ｄ１－ｄ）/２Ｈ＜０．９
　３．径方向断面肉厚Ｈと内径ｄの比が０．０５＜Ｈ／ｄ＜０．１５
　４．ころ大径Ｄｗ１と径方向断面肉厚Ｈの比が０．３＜Ｄｗ１/Ｈ＜０．６ 1. Ratio of roller length Lw and inner ring width B is 0.8 <Lw / B <1.2
2. 0.7 <(D1-d) / 2H <0.9, where inner ring inner diameter d, inner ring outer diameter D1, and inner ring large collar side height is (D1-d) / 2.
3. The ratio of the radial cross-sectional thickness H to the inner diameter d is 0.05 <H / d <0.15
4). The ratio of the roller large diameter Dw1 to the radial cross-sectional thickness H is 0.3 <Dw1 / H <0.6
　このような寸法規定された円すいころ軸受１は、内輪３の最少肉厚が非常に薄くなり、転がり軸受１に加わるラジアル荷重が大きくなると、円すいころ４が内輪３軌道面３ａをころがる際に内輪３が変形し、内輪３の軸孔に嵌めこまれる軸とのはめあい面が波打つ挙動を起こすことからクリープが生じる。 In the tapered roller bearing 1 with such dimensions defined, when the minimum thickness of the inner ring 3 becomes very thin and the radial load applied to the rolling bearing 1 increases, the tapered roller 4 rolls on the inner ring 3 raceway surface 3a. 3 is deformed, and creeping occurs because the fitting surface with the shaft fitted in the shaft hole of the inner ring 3 has a wavy behavior.
　このように、円すいころ軸受１においては、コンパクト性、接触角αの急こう配化、負荷容量アップを図ると、内輪３の肉厚が薄くなり、円すいころ４直下のはめあい面が変形を生じクリープが発生する。 As described above, in the tapered roller bearing 1, when the compactness, the steep gradient of the contact angle α, and the increase of the load capacity are achieved, the inner ring 3 is thinned, and the fitting surface immediately below the tapered roller 4 is deformed and creeped. Will occur.
　特許文献２のように、内輪３の小径側に軸方向に突出する小径側突出部１１を設けると、円すいころ４直下のはめあい面の変形防止に効果的であると考えられるが、どのような寸法関係に規定すれば、クリープの発生に効果的であるかは、特許文献２には一切開示がない。 As in Patent Document 2, it is considered that providing a small-diameter-side protruding portion 11 that protrudes in the axial direction on the small-diameter side of the inner ring 3 is effective in preventing deformation of the fitting surface directly below the tapered roller 4. Patent Document 2 does not disclose at all whether it is effective for the occurrence of creep if it is defined in the dimensional relationship.
　一般的に、クリープ対策としては、「内輪３の肉厚を増やす」、「円すいころ４の本数を減らす」、「はめあいしめしろ量を増やす」が挙げられる。 Generally, as countermeasures against creep, there are “increase the wall thickness of the inner ring 3”, “decrease the number of tapered rollers 4”, and “increase the amount of interference fit”.
　しかしながら、内輪３の肉厚を増やすとコンパクト性に劣り、円すいころ４の本数を減らすと負荷容量が低下する。 However, if the thickness of the inner ring 3 is increased, the compactness is inferior, and if the number of tapered rollers 4 is reduced, the load capacity is reduced.
　また、軸とのはめあいしめしろ量を増やすと、内輪３の肉厚が薄いために、フープ応力が増大しリング割れが生じる懸念がある。 Also, if the amount of interference fit with the shaft is increased, there is a concern that the hoop stress increases and ring cracking occurs because the inner ring 3 is thin.
　そこで、この発明は、保持器が、外輪の外輪軌道面や内輪の内輪軌道面に接触しないようにして、外輪の外輪軌道面や内輪の内輪軌道面に保持器が接触することによる傷や摩耗の発生を防止することができ、円すいころ直下のはめあい面の変形によるクリープの発生を抑制した、円すいころ軸受を提供することを課題とする。 Therefore, the present invention prevents scratches or wear caused by the cage coming into contact with the outer ring raceway surface of the outer ring or the inner ring raceway surface of the inner ring so that the cage does not come into contact with the outer ring raceway surface of the outer ring or the inner ring raceway surface of the inner ring. It is an object of the present invention to provide a tapered roller bearing that can prevent the occurrence of creep and suppress the occurrence of creep due to deformation of the fitting surface directly below the tapered roller.
　前記の課題を解決するために、この発明は、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すいころと、この複数の円すいころを所定の間隔で収容保持する複数のポケットを有する保持器とを備え、内輪の大径側端部と小径側端部のうち、大径側端部にのみ半径方向外方に突出する鍔部を有し、前記内輪の小径側に軸方向に突出する小径側突出部を設け、この小径側突出部の外径が、内輪の内輪軌道面の小径側端部の外径よりも内径側に位置し、前記小径側突出部の端面が、保持器の小径側の端面よりも小径側に突出し、接触角が３５°以上の高接触角である円すいころ軸受において、前記保持器が、軸方向に離れた大径リング部及び小径リング部と、大径リング部と小径リング部との間に所定の間隔で設けられた円すいころを収容保持する複数のポケットを区画する柱部とを備え、大径リング部の内周面と前記内輪の大径側端部の鍔部の外径面との間の隙間と、小径リング部の内周面と内輪の小径側突出部の外径面との間の隙間がいずれも、柱部と内輪の内輪軌道面との間の隙間よりも小さいことを特徴とする。 In order to solve the above problems, the present invention provides 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 an outer ring raceway surface between the outer ring raceway surface and the inner ring raceway surface. A plurality of tapered rollers arranged in a freely movable manner, and a cage having a plurality of pockets for accommodating and holding the plurality of tapered rollers at a predetermined interval, and comprising a large-diameter side end portion and a small-diameter side end portion of the inner ring The large-diameter end has a flange protruding outward in the radial direction only, and a small-diameter protrusion protruding in the axial direction is provided on the small-diameter side of the inner ring. The inner ring raceway surface is positioned on the inner diameter side of the outer diameter side end portion of the inner ring raceway surface, the end surface of the small diameter side projecting portion projects to the smaller diameter side than the end surface on the smaller diameter side of the cage, and the contact angle is 35 ° or more. In a tapered roller bearing having a high contact angle, the cage includes a large-diameter ring portion and a small diameter portion separated in the axial direction. A ring portion, and a column portion that divides a plurality of pockets for accommodating and holding tapered rollers provided at predetermined intervals between the large diameter ring portion and the small diameter ring portion, and an inner peripheral surface of the large diameter ring portion; Both the gap between the outer diameter surface of the flange at the large-diameter side end of the inner ring and the gap between the inner peripheral surface of the small-diameter ring part and the outer diameter surface of the small-diameter side protrusion of the inner ring are pillars. It is smaller than the clearance gap between a part and the inner ring raceway surface of an inner ring.
　前記大径リング部の内周面と前記内輪の大径側端部の鍔部の外径面との間の隙間と、小径リング部の内周面と内輪の小径側突出部の外径面との間の隙間が同一でもよい。 A gap between the inner peripheral surface of the large-diameter ring portion and the outer-diameter surface of the flange on the large-diameter side end of the inner ring, and the outer peripheral surface of the inner peripheral surface of the small-diameter ring portion and the small-diameter side protrusion of the inner ring The gap between them may be the same.
　前記内輪の内輪軌道面と小径側突出部の接合部にグリース溜り溝を設けてもよい。 A grease retaining groove may be provided at the joint between the inner ring raceway surface of the inner ring and the small-diameter side protruding portion.
　前記内輪の内径面の軸方向寸法を次式を満足するように規定することにより、円すいころ直下のはめあい面の変形によるクリープの発生を抑制することができる。
　　Ｑ＋Ｐ＞０．７Ｌｗ×ｃｏｓα
　但し、Ｐ：大鍔軸方向寸法、Ｌｗ×ｃｏｓα：円すいころ直下の軸方向寸法、Ｌｗ：円すいころ長さである。 By defining the axial dimension of the inner diameter surface of the inner ring so as to satisfy the following equation, the occurrence of creep due to the deformation of the fitting surface directly below the tapered roller can be suppressed.
Q + P> 0.7Lw × cosα
However, P is the size of the large saddle shaft direction, Lw × cos α is the axial size immediately below the tapered roller, and Lw is the length of the tapered roller.
　以上のように、この発明によれば、円すいころ軸受の回転中における保持器の振れまわり量が大きくなっても、保持器は外輪の外輪軌道面や内輪の内輪軌道面に接触しないので、外輪の外輪軌道面や内輪の内輪軌道面に保持器が接触することによる傷や摩耗の発生を防止することができ、また、円すいころ直下のはめあい面の変形によるクリープの発生を抑制することができる。 As described above, according to the present invention, the cage does not contact the outer ring raceway surface of the outer ring or the inner ring raceway surface of the inner ring even when the amount of swirling of the cage during rotation of the tapered roller bearing increases. Can prevent the cage from coming into contact with the outer ring raceway surface and the inner ring raceway surface of the inner ring, and can also prevent the occurrence of creep due to deformation of the fitting surface directly below the tapered roller. .
この発明の円すいころ軸受を保持器の柱部で切断した部分断面図である。It is the fragmentary sectional view which cut | disconnected the tapered roller bearing of this invention by the pillar part of the holder | retainer. この発明の円すいころ軸受の組付け状態を保持器のポケットの中心で切断した部分断面図である。It is the fragmentary sectional view which cut | disconnected the assembled state of the tapered roller bearing of this invention in the center of the pocket of a holder | retainer. 円すいころを示す図である。It is a figure which shows a tapered roller. 特許文献２の円すいころ軸受を保持器の柱部で切断した部分断面図である。It is the fragmentary sectional view which cut | disconnected the tapered roller bearing of patent document 2 with the pillar part of the holder | retainer. 特許文献３の円すいころ軸受を保持器の柱部で切断した部分断面図である。It is the fragmentary sectional view which cut | disconnected the tapered roller bearing of patent document 3 with the pillar part of the holder | retainer.
　以下、この発明の実施の形態を添付図面に基づいて説明する。
　この発明に係る円すいころ軸受１１は、接触角αが３５°以上という急勾配のものであり、図１及び図２に示す実施形態の円すいころ軸受１１の接触角αは４５°である。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
The tapered roller bearing 11 according to the present invention has a steep contact angle α of 35 ° or more, and the tapered roller bearing 11 of the embodiment shown in FIGS. 1 and 2 has a contact angle α of 45 °.
　この発明に係る円すいころ軸受１１は、内周面に外輪軌道面１２ａを有する外輪１２と、外周面に内輪軌道面１３ａを有する内輪１３と、前記外輪軌道面１２ａと前記内輪軌道面１３ａとの間に転動自在に配置される複数の円すいころ１４と、この複数の円すいころ１４を所定の間隔で収容保持する複数のポケットＰを有する保持器２０とを備え、内輪１３の大径側端部と小径側端部のうち、大径側端部にのみ半径方向外方に突出する鍔部１３ｂを有する。 The tapered roller bearing 11 according to the present invention includes an outer ring 12 having an outer ring raceway surface 12a on an inner peripheral surface, an inner ring 13 having an inner ring raceway surface 13a on an outer peripheral surface, and the outer ring raceway surface 12a and the inner ring raceway surface 13a. A plurality of tapered rollers 14 disposed so as to be able to roll between, and a retainer 20 having a plurality of pockets P for accommodating and holding the plurality of tapered rollers 14 at a predetermined interval. Of the portion and the small-diameter side end portion, only the large-diameter side end portion has a flange portion 13b protruding outward in the radial direction.
　前記内輪１３の小径側端部には、軸方向に突出する小径側突出部１３ｃを設けている。 A small-diameter protruding portion 13c protruding in the axial direction is provided at the small-diameter side end of the inner ring 13.
　この小径側突出部１３ｃの外径Ｄ1は、内輪１３の内輪軌道面１３ａの小径側端部の外径Ｄ2よりも内径側に位置し、前記小径側突出部１３ｃの端面１３ｅが、保持器２０の小径側の端面２０ｄよりも小径側に突出している。 Outer diameter D 1 of the small diameter side protruding portion 13c is located on the inner diameter side than the outer diameter D 2 of the smaller diameter end of the inner ring raceway surface 13a of the inner ring 13, the end surface 13e of the small diameter side protruding portion 13c is held It protrudes to the smaller diameter side than the end surface 20d on the smaller diameter side of the vessel 20.
　前記小径側突出部１３ｃの外径面１３ｄは、内輪１３の軸に対して平行面に形成されている。 The outer diameter surface 13d of the small diameter side protruding portion 13c is formed in a plane parallel to the axis of the inner ring 13.
　このように、内輪１３の小径側端部に、保持器２０の小径側の端面２０ｄよりも小径側に突出する小径側突出部１３ｃを設けると、外輪１２を組付ける際に、図２に示すように、外輪１２の小径側の内周面に、内輪１３の小径側突出部１３ｃの端面１３ｅに当接するリング間座２１を嵌め入れることにより、高接触角の外輪１２のふらつきがリング間座２１によって抑制することができるので、外輪１２が安定し、軸受の組幅寸法Ｔの測定が正確に行える。 As shown in FIG. 2, when the outer ring 12 is assembled when the small-diameter side end portion of the inner ring 13 is provided with the small-diameter side protruding portion 13c that protrudes to the small-diameter side from the end surface 20d on the small-diameter side of the cage 20. As described above, the ring spacer 21 that contacts the end surface 13e of the small-diameter-side protruding portion 13c of the inner ring 13 is fitted into the inner peripheral surface of the outer ring 12 on the small-diameter side. 21, the outer ring 12 is stabilized and the bearing assembly width dimension T can be accurately measured.
　前記保持器２０は、軸方向に離れた大径リング部２０ａ及び小径リング部２０ｂと、大径リング部２０ａと小径リング部２０ｂとの間に所定の間隔で設けられた円すいころ１４を収容保持する複数のポケットＰを区画する柱部２０ｃとを備えている。 The cage 20 accommodates and holds large-diameter ring portions 20a and small-diameter ring portions 20b that are separated in the axial direction, and tapered rollers 14 that are provided between the large-diameter ring portion 20a and the small-diameter ring portion 20b at a predetermined interval. And a column portion 20c that partitions a plurality of pockets P.
　この発明では、図１に示すように、保持器２０の小径リング部２０ｂの内周面と内輪１３の小径側突出部１３ｃの外径面との間の隙間ａと、保持器２０の大径リング部２０ａの内周面と内輪１３の大径側端部の鍔部１３ｂの外径面との間の隙間ｂを、保持器１０の柱部２０ｃと内輪１３の内輪軌道面１３ａ及び外輪１２の外輪軌道面１２ａとの間の隙間ｃ、ｄよりも小さくして、保持器１０の柱部２０ｃが外輪１２の外輪軌道面１２ａや内輪１３の内輪軌道面１３ａに接触する前に、保持器２０の両端が、内輪１３の大径側端部の鍔部１３ｂの外径面と内輪１３の小径側突出部１３ｃの外径面に接触し、この接触による案内によって外輪１２の外輪軌道面１２ａや内輪１３の内輪軌道面１３ａの損傷が防止される。 In this invention, as shown in FIG. 1, the clearance a between the inner peripheral surface of the small-diameter ring portion 20 b of the cage 20 and the outer-diameter surface of the small-diameter side protruding portion 13 c of the inner ring 13, and the large diameter of the cage 20. A gap b between the inner peripheral surface of the ring portion 20a and the outer diameter surface of the flange portion 13b at the end on the large diameter side of the inner ring 13 is used to form the clearance 20b of the retainer 10 and the inner ring raceway surface 13a and outer ring 12 of the inner ring 13. The cage 20 is made smaller than the gaps c and d between the outer ring raceway surface 12a and the retainer 10 before the column portion 20c of the cage 10 contacts the outer ring raceway surface 12a of the outer ring 12 and the inner ring raceway surface 13a of the inner ring 13. Both ends of 20 contact the outer diameter surface of the flange portion 13b at the large-diameter side end of the inner ring 13 and the outer diameter surface of the small-diameter protruding portion 13c of the inner ring 13, and the outer ring raceway surface 12a of the outer ring 12 is guided by this contact. Further, damage to the inner ring raceway surface 13a of the inner ring 13 is prevented.
　具体的な各隙間ｃ、ｄ、ａ、ｂの関係は、ｃ、ｄ＞ａ＝ｂである。 Specific relations between the gaps c, d, a, and b are c and d> a = b.
　また、隙間ａ、ｂの管理を行ない易くするために、内輪１３の小径側突出部１３ｃの外径面と、内輪１３の大径側端部の鍔部１３ｂの外径面を軸方向に平行にすることが望ましい。 Further, in order to facilitate the management of the gaps a and b, the outer diameter surface of the small diameter side protruding portion 13c of the inner ring 13 and the outer diameter surface of the flange portion 13b of the large diameter side end portion of the inner ring 13 are parallel to the axial direction. It is desirable to make it.
　また、隙間ａ、ｂをいずれも同じ幅にすることにより、保持器２０の両端を内輪１３に対して支持できるので、片側で支持する場合よりも、保持器２０に加わるモーメント荷重を軽減することができる。 In addition, by setting the gaps a and b to the same width, both ends of the cage 20 can be supported with respect to the inner ring 13, so that the moment load applied to the cage 20 can be reduced as compared with the case where it is supported on one side. Can do.
　前記内輪１３の内輪軌道面１３ａと小径側突出部１３ｃの接合部には、グリース溜り溝１３ｆを形成している。グリース潤滑を採用する場合に、グリース溜り溝１３ｆにグリースを溜めることによって、内輪１３の内輪軌道面１３ａの小径側の潤滑不良を軽減することができる。 A grease retaining groove 13f is formed at a joint portion between the inner ring raceway surface 13a of the inner ring 13 and the small diameter side protruding portion 13c. When the grease lubrication is employed, the lubrication failure on the small diameter side of the inner ring raceway surface 13a of the inner ring 13 can be reduced by collecting the grease in the grease retaining groove 13f.
　また、グリース溜り溝１３ｆを、内輪１３の内輪軌道面１３ａと小径側突出部１３ｃの接合部に設けると、円すいころ軸受１１を垂直方向に立てた際、円すいころ１４の小径側のぬすみ部が、グリース溜り溝１３ｆに引っ掛かり、円すいころ４を保持することができるので、グリース溜り溝１３ｆが円すいころ４を保持する小鍔として機能する。 Further, when the grease retaining groove 13f is provided at the joint between the inner ring raceway surface 13a of the inner ring 13 and the small-diameter side protruding portion 13c, when the tapered roller bearing 11 is erected in the vertical direction, the small-diameter side thin portion of the tapered roller 14 is provided. Since the tapered roller 4 can be held by being caught in the grease retaining groove 13f, the grease retaining groove 13f functions as a small scissors that retains the tapered roller 4.
　次に、この発明の発明者は、内輪１３の内径面における軸方向寸法の関係、すなわち、大鍔軸方向寸法Ｐと、円すいころ１４直下の軸方向寸法（Ｌｗ×ｃｏｓα）と、小径側突出部１３ｃの軸方向寸法Ｑの関係を、下記のように規定することにより、クリープの発生を抑制することができるということを見出した。 Next, the inventor of the present invention relates to the relationship between the axial dimensions on the inner diameter surface of the inner ring 13, that is, the large flange axial dimension P, the axial dimension directly below the tapered roller 14 (Lw × cos α), and the small-diameter side protrusion. It has been found that the occurrence of creep can be suppressed by defining the relationship of the axial dimension Q of the portion 13c as follows.
　その関係とは、
　　Ｑ＋Ｐ＞０．７Ｌｗ×ｃｏｓα
　　Ｑ＞（０．７Ｌｗ×ｃｏｓα）－Ｐ
である。 The relationship is
Q + P> 0.7Lw × cosα
Q> (0.7 Lw × cos α) −P
It is.
　上記の関係式によって、クリープの発生が抑制できるということを下記条件において検証した。
・軸とのはめあい：ラジアル軸受（ＪＩＳ０級）に対してｋ６～ｍ６程度（例えば、内径φ２４０の場合はめあいしめしろ４ｕｍ～７１ｕｍを指す）
・転動体と内輪軌道面の最大接触面圧　２パターン：１５００ＭＰａ、２５００ＭＰａ It was verified under the following conditions that the occurrence of creep can be suppressed by the above relational expression.
・ Fitting with shaft: about k6 to m6 for radial bearings (JIS class 0) (for example, when the inner diameter is φ240, it indicates a fitting margin of 4 um to 71 um)
・ Maximum contact surface pressure between rolling elements and inner ring raceway surface 2 patterns: 1500 MPa, 2500 MPa
　検証結果は、表１の通りであり、内輪１３の内径面において、転動体直下の軸方向の幅寸法（Ｌｗ×ｃｏｓα）の０．７倍以上の非転動体直下の幅寸法（Ｑ＋Ｐ）があれば、クリープの抑制ができる。 The verification results are as shown in Table 1. On the inner diameter surface of the inner ring 13, the width dimension (Q + P) directly below the non-rolling element is 0.7 times or more the axial width dimension (Lw × cos α) immediately below the rolling element. If there is, creep can be suppressed.
Figure JPOXMLDOC01-appb-T000001
Figure JPOXMLDOC01-appb-T000001
　この発明は前述した実施形態に何ら限定されるものではなく、この発明の要旨を逸脱しない範囲において、さらに種々の形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内の全ての変更を含む。 The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. The scope of the present invention is claimed. The equivalent meanings recited in the claims, and all modifications within the scope.
１０　　　：保持器
１１　　　：軸受
１２　　　：外輪
１２ａ　　：外輪軌道面
１３　　　：内輪
１３ａ　　：内輪軌道面
１３ｂ　　：鍔部
１３ｃ　　：小径側突出部
１３ｄ　　：外径面
１３ｅ　　：端面
１３ｆ　　：グリース溜り溝
２０　　　：保持器
２０ａ　　：大径リング部
２０ｂ　　：小径リング部
２０ｃ　　：柱部
２０ｄ　　：端面
２１　　　：リング間座
Ｐ　　　　：ポケット DESCRIPTION OF SYMBOLS 10: Cage 11: Bearing 12: Outer ring 12a: Outer ring raceway surface 13: Inner ring 13a: Inner ring raceway surface 13b: ridge part 13c: Small diameter side protrusion part 13d: Outer diameter surface 13e: End face 13f: Grease pool groove 20: Cage 20a: Large-diameter ring portion 20b: Small-diameter ring portion 20c: Column portion 20d: End face 21: Ring spacer P: Pocket

Claims (4)

  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すいころと、この複数の円すいころを所定の間隔で収容保持する複数のポケットを有する保持器とを備え、内輪の大径側端部と小径側端部のうち、大径側端部にのみ半径方向外方に突出する鍔部を有し、前記内輪の小径側に軸方向に突出する小径側突出部を設け、この小径側突出部の外径が、内輪の内輪軌道面の小径側端部の外径よりも内径側に位置し、前記小径側突出部の端面が、保持器の小径側の端面よりも小径側に突出し、接触角が３５°以上の高接触角である円すいころ軸受において、前記保持器が、軸方向に離れた大径リング部及び小径リング部と、大径リング部と小径リング部との間に所定の間隔で設けられた円すいころを収容保持する複数のポケットを区画する柱部とを備え、大径リング部の内周面と前記内輪の大径側端部の鍔部の外径面との間の隙間と、小径リング部の内周面と内輪の小径側突出部の外径面との間の隙間がいずれも、柱部と内輪の内輪軌道面との間の隙間よりも小さい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 arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface, A cage having a plurality of pockets for accommodating and holding a plurality of tapered rollers at a predetermined interval, and out of the large-diameter side end and the small-diameter side end of the inner ring only radially outward. A small-diameter-side protruding portion that protrudes in the axial direction is provided on the small-diameter side of the inner ring, and the outer diameter of the small-diameter-side protruding portion is greater than the outer diameter of the small-diameter end of the inner ring raceway surface of the inner ring. In the tapered roller bearing in which the end surface of the small-diameter side protruding portion protrudes to the small-diameter side from the end surface on the small-diameter side of the cage, and the contact angle is a high contact angle of 35 ° or more. Is a large-diameter ring portion and a small-diameter ring portion that are separated in the axial direction, and a large-diameter ring portion and a small-diameter ring portion. Between the inner peripheral surface of the large-diameter ring portion and the flange portion of the large-diameter side end portion of the inner ring. The gap between the inner surface of the small diameter ring part and the outer diameter surface of the small diameter side protruding part of the inner ring is more than the gap between the column part and the inner ring raceway surface of the inner ring. Tapered roller bearings that are also small.
  2. 　前記大径リング部の内周面と前記内輪の大径側端部の鍔部の外径面との間の隙間と、小径リング部の内周面と内輪の小径側突出部の外径面との間の隙間が同一であることを特徴とする請求項１に記載の円すいころ軸受。 A gap between the inner peripheral surface of the large-diameter ring portion and the outer-diameter surface of the flange on the large-diameter side end of the inner ring, and the outer peripheral surface of the inner peripheral surface of the small-diameter ring portion and the small-diameter side protrusion of the inner ring The tapered roller bearing according to claim 1, wherein a gap between the two and the same is the same.
  3. 　前記内輪の内輪軌道面と小径側突出部の接合部にグリース溜り溝を設けたことを特徴とする請求項１又は２に記載の円すいころ軸受。 3. The tapered roller bearing according to claim 1, wherein a grease retaining groove is provided at a joint portion between the inner ring raceway surface of the inner ring and the small-diameter side protruding portion.
  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、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すいころと、この複数の円すいころを所定の間隔で収容保持する複数のポケットを有する保持器とを備え、内輪の大径側端部と小径側端部のうち、大径側端部にのみ半径方向外方に突出する鍔部を有し、前記内輪の小径側に軸方向に突出する小径側突出部を設け、この小径側突出部の外径が、内輪の内輪軌道面の小径側端部の外径よりも内径側に位置し、前記小径側突出部の端面が、保持器の小径側の端面よりも小径側に突出し、接触角が３５°以上の高接触角である円すいころ軸受において、内輪の内径面の軸方向寸法を次式を満足するように規定したことを特徴とする円すいころ軸受。
    　　Ｑ＋Ｐ＞０．７Ｌｗ×ｃｏｓα
    　　但し、Ｐ：大鍔軸方向寸法
    　　　　　Ｌｗ×ｃｏｓα：円すいころ直下の軸方向寸法
    　　　　　Ｌｗ：円すいころ長さ     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 arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface, A cage having a plurality of pockets for accommodating and holding a plurality of tapered rollers at a predetermined interval, and out of the large-diameter side end and the small-diameter side end of the inner ring only radially outward. A small-diameter-side protruding portion that protrudes in the axial direction is provided on the small-diameter side of the inner ring, and the outer diameter of the small-diameter-side protruding portion is greater than the outer diameter of the small-diameter end of the inner ring raceway surface of the inner ring. In the tapered roller bearing which is located on the inner diameter side, the end surface of the small diameter side protruding portion protrudes to the small diameter side from the end surface on the small diameter side of the cage, and the contact angle is a high contact angle of 35 ° or more, the inner diameter of the inner ring A tapered roller bearing characterized in that the axial dimension of the surface is defined to satisfy the following formula.
    Q + P> 0.7Lw × cosα
    However, P: Large axial direction dimension Lw × cos α: Axial dimension directly below tapered roller Lw: Tapered roller length
PCT/JP2016/066290 2015-06-05 2016-06-01 Tapered roller bearing WO2016194981A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2015114486 2015-06-05
JP2015-114486 2015-06-05
JP2016067478A JP6329198B2 (en) 2015-06-05 2016-03-30 Tapered roller bearing
JP2016-067478 2016-03-30

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113167320A (en) * 2018-12-07 2021-07-23 Ntn株式会社 Tapered roller bearing

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0538421U (en) * 1991-10-23 1993-05-25 光洋精工株式会社 Tapered roller bearing
JPH1089353A (en) * 1996-09-19 1998-04-07 Koyo Seiko Co Ltd Tapered roller bearing
JP2000304054A (en) * 1999-04-16 2000-10-31 Nsk Ltd Tapered roller bearing
JP2009097601A (en) * 2007-10-16 2009-05-07 Ntn Corp Punching cage and separable roller bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0538421U (en) * 1991-10-23 1993-05-25 光洋精工株式会社 Tapered roller bearing
JPH1089353A (en) * 1996-09-19 1998-04-07 Koyo Seiko Co Ltd Tapered roller bearing
JP2000304054A (en) * 1999-04-16 2000-10-31 Nsk Ltd Tapered roller bearing
JP2009097601A (en) * 2007-10-16 2009-05-07 Ntn Corp Punching cage and separable roller bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113167320A (en) * 2018-12-07 2021-07-23 Ntn株式会社 Tapered roller bearing
CN113167320B (en) * 2018-12-07 2022-11-11 Ntn株式会社 Tapered roller bearing

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