JP2013024354A - Rotary shaft device - Google Patents

Rotary shaft device Download PDF

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JP2013024354A
JP2013024354A JP2011161449A JP2011161449A JP2013024354A JP 2013024354 A JP2013024354 A JP 2013024354A JP 2011161449 A JP2011161449 A JP 2011161449A JP 2011161449 A JP2011161449 A JP 2011161449A JP 2013024354 A JP2013024354 A JP 2013024354A
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Prior art keywords
ring
outer ring
inner ring
oil
fitted
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Japanese (ja)
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Yu Yasuda
遊 安田
Yozo Taniguchi
陽三 谷口
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JTEKT Corp
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JTEKT Corp
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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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Abstract

PROBLEM TO BE SOLVED: To prevent the seal property of a lip part by suppressing the occurrence of oil sludge by suppressing temperature elevation of lubricating oil around the lip part.SOLUTION: A rolling bearing includes: a ring-shaped outer ring 21; an inner ring 22 disposed at an inner peripheral side of the outer ring 21; and a rolling body 24 which rolls between the outer ring 21 and the inner ring 22. In a rotary shaft device, the outer ring 21 is fitted and fixed to a housing 11, the inner ring 22 is fitted to a rotary shaft, an oil seal 60 is mounted to the inner periphery of the outer ring 21, and a lip part 64 at an inner peripheral side of the oil seal 60 is brought into slide-contact with the inner ring 22. An annular groove is formed for storing lubricating oil in the outer circumference of the inner ring 22 between the rolling body 24 and the oil seal 60, and the annular groove has a slope 22e whose depth becomes shallower gradually toward the rolling body 24.

Description

本発明は、回転軸を転がり軸受を介して回転可能に軸承した回転軸装置に関する。   The present invention relates to a rotary shaft device that rotatably supports a rotary shaft via a rolling bearing.

図４に示すように、自動車のディファレンシャル装置１００は、ディファレンシャルケース１０１に転がり軸受１１０を介して回転軸１２０を回転可能に軸承し、回転軸１２０の一端に形成されたピニオンギヤ１２１を図略のリングギヤに噛合させている。転がり軸受１１０は、外輪１１１と、内輪１１２、１１３と、玉１１４、１１５と、保持器１１６、１１７とからなり、外輪１１１の内周にオイルシール１３０が圧入嵌合され、オイルシール１３０の内周側のリップ部１３１、１３２が内輪１１２の外周に摺接している。   As shown in FIG. 4, a differential apparatus 100 for an automobile supports a rotary shaft 120 rotatably on a differential case 101 via a rolling bearing 110, and a pinion gear 121 formed at one end of the rotary shaft 120 is a ring gear (not shown). Is engaged. The rolling bearing 110 includes an outer ring 111, inner rings 112 and 113, balls 114 and 115, and cages 116 and 117. An oil seal 130 is press-fitted to the inner periphery of the outer ring 111. The peripheral lip portions 131 and 132 are in sliding contact with the outer periphery of the inner ring 112.

特許第４５２５２０８号Japanese Patent No. 45525208

リップ部１３１と内輪１１２間の摩擦により発熱し、リップ部１３１の周辺の潤滑油に熱が伝わり、潤滑油の温度が上昇するとオイルスラッジが発生しやすくなり、リップ部１３１の密封性が低下する。   Heat is generated due to friction between the lip 131 and the inner ring 112, and heat is transmitted to the lubricating oil around the lip 131. When the temperature of the lubricating oil rises, oil sludge is easily generated, and the sealing performance of the lip 131 is reduced. .

本発明は上述した問題点を解決するためになされたもので、その目的は、リップ部周辺の潤滑油の温度の上昇を抑えてオイルスラッジの発生を抑え、リップ部の密封性の低下を防ぐ。   The present invention has been made to solve the above-described problems, and its purpose is to suppress an increase in the temperature of the lubricating oil around the lip portion, thereby suppressing the generation of oil sludge and preventing a decrease in the sealing performance of the lip portion. .

請求項１に記載の発明は、転がり軸受は、リング状の外輪と、この外輪の内周側に配置される内輪と、前記外輪および前記内輪間で転動する転動体とからなり、前記外輪をハウジングに嵌合固定し、前記内輪を前記回転軸に嵌合し、前記外輪の内周にオイルシールを取付け、オイルシールの内周側のリップ部を前記内輪に摺接させた回転軸装置において、
前記転動体および前記リップ部間で前記内輪の外周に潤滑油が貯留する環状溝を形成し、この環状溝は、前記転動体に向かって溝深さが次第に浅くなる傾斜面を有するものである。 According to the first aspect of the present invention, the rolling bearing includes a ring-shaped outer ring, an inner ring disposed on the inner peripheral side of the outer ring, and a rolling element that rolls between the outer ring and the inner ring. A rotating shaft device in which the inner ring is fitted to the rotating shaft, an oil seal is attached to the inner periphery of the outer ring, and the lip portion on the inner peripheral side of the oil seal is in sliding contact with the inner ring. In
An annular groove for storing lubricating oil is formed on the outer periphery of the inner ring between the rolling element and the lip portion, and the annular groove has an inclined surface in which the groove depth gradually decreases toward the rolling element. .

本発明によれば、内輪を回転させると、リップ部周辺の潤滑油は、環状溝を経て転動体側へ流れ、リップ部周辺には新たな潤滑油が供給されるので、リップ部周辺の潤滑油の温度の上昇が抑えられてオイルスラッジの発生が抑えられ、リップ部の密封性の低下を防ぐことができる。   According to the present invention, when the inner ring is rotated, the lubricating oil around the lip portion flows to the rolling element side through the annular groove, and new lubricating oil is supplied around the lip portion. The rise in the temperature of the oil is suppressed, the generation of oil sludge is suppressed, and the deterioration of the sealing performance of the lip portion can be prevented.

本発明の一実施形態における回転軸装置の縦断面図The longitudinal cross-sectional view of the rotating shaft apparatus in one Embodiment of this invention 本発明の一実施形態における図１の要部拡大断面図The principal part expanded sectional view of FIG. 1 in one Embodiment of this invention 本発明の一実施形態における図２の要部拡大断面図The principal part expanded sectional view of FIG. 2 in one Embodiment of this invention 従来の回転軸装置の断面図Sectional view of a conventional rotary shaft device

本発明の一実施形態を、図１乃至図３にもとづいて説明する。図１は、回転軸装置の縦断面図、図２は、図１の要部拡大断面図であり、図３は、図２の要部拡大断面図である。   An embodiment of the present invention will be described with reference to FIGS. 1 to 3. 1 is a longitudinal sectional view of the rotating shaft device, FIG. 2 is an enlarged sectional view of a main part of FIG. 1, and FIG. 3 is an enlarged sectional view of a main part of FIG.

図１および図２において、自動車のディファレンシャル装置は、ディファレンシャルケース１１と、このディファレンシャルケース１１に軸線Ｐ回りに回転可能に軸承されたリングギヤ８０と、回転軸装置１０とを有する。   1 and 2, the vehicle differential apparatus includes a differential case 11, a ring gear 80 that is rotatably supported around the axis P by the differential case 11, and the rotary shaft apparatus 10.

回転軸装置１０は、ディファレンシャルケース１１の一部と、このディファレンシャルケース１１の一部に取り付けられた転がり軸受２０と、この転がり軸受２０を介してディファレンシャルケース１１に回転可能に軸承されたピニオン軸４０と、ピニオン軸４０の一端に取付けられたコンパニオンフランジ５０とを有している。前記リングギヤ８０の回転軸線とピニオン軸４０の回転軸線は、互いに立体的に交差している。   The rotary shaft device 10 includes a part of a differential case 11, a rolling bearing 20 attached to a part of the differential case 11, and a pinion shaft 40 rotatably supported by the differential case 11 via the rolling bearing 20. And a companion flange 50 attached to one end of the pinion shaft 40. The rotation axis of the ring gear 80 and the rotation axis of the pinion shaft 40 intersect each other three-dimensionally.

ディファレンシャルケース１１にはピニオン軸４０の軸線方向に貫通した貫通穴１２が形成され、この貫通穴１２に転がり軸受２０が嵌合されている。転がり軸受２０は、貫通穴１２に嵌合される外輪２１と、外輪２１の内周側に配置される内輪２２、３２と、外輪２１および内輪２２、３２間を転動する玉２４、３４と、玉２４、３４を回転可能に保持する保持器２３、３３とからなっている。転がり軸受２０は、一つの外輪２１に対し、二つの内輪２２、３２を軸方向に配置した一対のアンギュラ玉軸受である。   The differential case 11 is formed with a through hole 12 penetrating in the axial direction of the pinion shaft 40, and a rolling bearing 20 is fitted into the through hole 12. The rolling bearing 20 includes an outer ring 21 fitted in the through hole 12, inner rings 22 and 32 disposed on the inner peripheral side of the outer ring 21, and balls 24 and 34 that roll between the outer ring 21 and the inner rings 22 and 32. , And retainers 23 and 33 for holding the balls 24 and 34 rotatably. The rolling bearing 20 is a pair of angular ball bearings in which two inner rings 22 and 32 are arranged in the axial direction with respect to one outer ring 21.

外輪２１の内周に２つの外輪側軌道面２１ａ、３１ａが形成され、これら外輪側軌道面２１ａ、３１ａに対応する位置で内輪２２、３２の外周に内輪側軌道面２２ａ、３２ａが形成されている。外輪２１は、内輪２２に対し内輪２３と反対側へ軸方向に突出した突起部を有し、さらにこの突起部に対し外径方向へ突出したフランジ部を有する。外輪２１の軸方向に突出した突起部の内周に、後述するオイルシール６０が嵌合固定される第４の嵌合面２１ｂが形成されている。内輪２２の外周には、内輪側軌道面２２ａを挟んで内輪３２側に内輪２２の軸線に対し傾斜したテーパ面２２ｂが形成され、内輪側軌道面２２ａを挟んで内輪３２と反対側に内輪２２の軸線と平行な平行面２２ｃが形成されている。内輪３２の外周には、内輪側軌道面３２ａを挟んで内輪２２側に内輪３２の軸線に対し傾斜したテーパ面３２ｂが形成され、内輪側軌道面３２ａを挟んで内輪２２と反対側に内輪３２の軸線と平行な平行面３２ｃが形成されている。内輪２２、３２の内周には、ピニオン軸４０の後述する第１の嵌合面４２に嵌合される第１の被嵌合面が形成されている。   Two outer ring side raceways 21a, 31a are formed on the inner circumference of the outer ring 21, and inner ring side raceways 22a, 32a are formed on the outer circumference of the inner rings 22, 32 at positions corresponding to these outer ring side raceways 21a, 31a. Yes. The outer ring 21 has a protruding portion that protrudes in the axial direction toward the opposite side of the inner ring 23 with respect to the inner ring 22, and further has a flange portion that protrudes in the outer diameter direction with respect to the protruding portion. A fourth fitting surface 21b to which an oil seal 60 (to be described later) is fitted and fixed is formed on the inner periphery of the protruding portion protruding in the axial direction of the outer ring 21. On the outer periphery of the inner ring 22, a tapered surface 22b inclined with respect to the axis of the inner ring 22 is formed on the inner ring 32 side with the inner ring side raceway surface 22a in between, and the inner ring 22 on the opposite side of the inner ring 32 with the inner ring side raceway surface 22a in between. A parallel surface 22c parallel to the axis is formed. On the outer periphery of the inner ring 32, a tapered surface 32b inclined with respect to the axis of the inner ring 32 is formed on the inner ring 22 side with the inner ring side raceway surface 32a interposed therebetween, and the inner ring 32 on the opposite side of the inner ring 22 with the inner ring side raceway surface 32a interposed therebetween. A parallel surface 32c parallel to the axis is formed. A first fitted surface that is fitted to a first fitting surface 42 of the pinion shaft 40 described later is formed on the inner circumference of the inner rings 22 and 32.

ピニオン軸４０のリングギヤ８０側の他端には、リングギヤ８０と噛合うピニオンギヤ４１が形成され、ピニオン軸４０の一端には、ネジ部４５が形成されている。ピニオン軸４０には、ピニオンギヤ４１およびネジ部４５間でピニオンギヤ４１側から順に第１の嵌合面４２、スプライン４４が形成されている。スプライン４４は、第１の嵌合面４２よりも小径である。ピニオンギヤ４１および第１の嵌合面４２間には第１の段部が形成され、第１の嵌合面４２およびスプライン４４間には第２の段部が形成されている。   A pinion gear 41 that meshes with the ring gear 80 is formed at the other end of the pinion shaft 40 on the ring gear 80 side, and a screw portion 45 is formed at one end of the pinion shaft 40. A first fitting surface 42 and a spline 44 are formed on the pinion shaft 40 in order from the pinion gear 41 side between the pinion gear 41 and the screw portion 45. The spline 44 has a smaller diameter than the first fitting surface 42. A first step portion is formed between the pinion gear 41 and the first fitting surface 42, and a second step portion is formed between the first fitting surface 42 and the spline 44.

第１の段部に内輪３２のピニオンギヤ４１側の端面が当接し、第２の段部にコンパニオンフランジ５０のピニオンギヤ４１側の後述する端面５３が隙間を持って対向する。スプライン４４には、コンパニオンフランジ５０が嵌合され、コンパニオンフランジ５０のピニオンギヤ４１側の後述する端面５３は、内輪２２のピニオンギヤ４１と反対側の端面に当接する。ネジ部４５には、ワッシャ５６が嵌め込まれ、さらにナット５８が螺合されている。ナット５８を締めることにより、内輪２２、３２は、第１の段部およびコンパニオンフランジ５０の後述する端面５３間で挟み込まれる。   An end surface of the inner ring 32 on the pinion gear 41 side contacts the first step portion, and an end surface 53 described later on the pinion gear 41 side of the companion flange 50 faces the second step portion with a gap. A companion flange 50 is fitted to the spline 44, and an end surface 53, which will be described later, on the pinion gear 41 side of the companion flange 50 abuts on an end surface of the inner ring 22 opposite to the pinion gear 41. A washer 56 is fitted into the screw portion 45, and a nut 58 is screwed. By tightening the nut 58, the inner rings 22, 32 are sandwiched between the first stepped portion and the end face 53 described later of the companion flange 50.

コンパニオンフランジ５０は、円筒状で、この円筒状の一端に外径方向へ突出したフランジ部を有する。円筒状の外周には、第３の嵌合面５１が形成され、この第３の嵌合面５１のフランジ部側にはスリンガー７０が嵌合固定されている。コンパニオンフランジ５０のピニオンギヤ４１側には、内輪２２に当接する端面５３を有する。コンパニオンフランジ５０のピニオンギヤ４１と反対側の一端には、図略の伝達軸がボルト等で連結され、エンジンからの回転動力が伝達されるようになっている。   The companion flange 50 has a cylindrical shape, and has a flange portion protruding in the outer diameter direction at one end of the cylindrical shape. A third fitting surface 51 is formed on the outer periphery of the cylindrical shape, and a slinger 70 is fitted and fixed to the flange portion side of the third fitting surface 51. On the side of the pinion gear 41 of the companion flange 50, an end face 53 that abuts against the inner ring 22 is provided. A transmission shaft (not shown) is connected to one end of the companion flange 50 on the side opposite to the pinion gear 41 with a bolt or the like, so that rotational power from the engine is transmitted.

図２および図３に示すように、オイルシール６０は、外輪２１の第４の嵌合面２１ｂに嵌合固定され、オイルシール６０の内周側の第１のリップ部６４および第２のリップ部６５は、内輪２２の平行面２２ｃに摺接している。オイルシール６０は、金属製の芯金６１と、芯金６１に加硫接着されたゴム製のシール本体６２とからなっている。シール本体６２の内周側に第１のリップ部６４および第２のリップ部６５が形成され、シール本体６２のスリンガー７０側の側面に第３のリップ部６３が形成されている。第３のリップ部６３は、スリンガー７０のピニオンギヤ４１側の側面に摺接している。   As shown in FIGS. 2 and 3, the oil seal 60 is fitted and fixed to the fourth fitting surface 21 b of the outer ring 21, and the first lip portion 64 and the second lip on the inner peripheral side of the oil seal 60. The part 65 is in sliding contact with the parallel surface 22 c of the inner ring 22. The oil seal 60 includes a metal core 61 and a rubber seal body 62 vulcanized and bonded to the core 61. A first lip portion 64 and a second lip portion 65 are formed on the inner peripheral side of the seal body 62, and a third lip portion 63 is formed on the side surface of the seal body 62 on the slinger 70 side. The third lip portion 63 is in sliding contact with the side surface of the slinger 70 on the pinion gear 41 side.

外輪２１の第４の嵌合面２１ｂには、玉２４およびオイルシール６０間で第１の環状溝が形成され、この第１の環状溝は、内輪２２の回転軸線に対し垂直な第１の垂直面２１ｄと、第１の環状溝の深さが玉２４側に向かって次第に浅くなるように内輪２２の回転軸線に対し傾斜した第１の傾斜面２１ｅとで構成されている。内輪２２の平行面２２ｃには、玉２４およびオイルシール６０間で第２の環状溝が形成され、この第２の環状溝は、内輪２２の回転軸線に対し垂直な第２の垂直面２２ｄと、第２の環状溝の深さが玉２４側に向かって次第に浅くなるように内輪２２の回転軸線に対し傾斜した第２の傾斜面２２ｅとで構成されている。第１の環状溝は、第２の環状溝に対し玉２４側に位置し、第１の垂直面２１ｄの延長線上に第２の傾斜面２２ｅが存在する。   On the fourth fitting surface 21 b of the outer ring 21, a first annular groove is formed between the ball 24 and the oil seal 60, and the first annular groove is a first perpendicular to the rotation axis of the inner ring 22. A vertical surface 21d and a first inclined surface 21e inclined with respect to the rotation axis of the inner ring 22 so that the depth of the first annular groove gradually decreases toward the ball 24 side. A second annular groove is formed between the ball 24 and the oil seal 60 on the parallel surface 22 c of the inner ring 22, and the second annular groove is connected to a second vertical surface 22 d perpendicular to the rotation axis of the inner ring 22. The second annular groove is composed of a second inclined surface 22e that is inclined with respect to the rotation axis of the inner ring 22 so that the depth of the second annular groove gradually decreases toward the ball 24 side. The first annular groove is located on the ball 24 side with respect to the second annular groove, and the second inclined surface 22e exists on the extended line of the first vertical surface 21d.

図１に示すように、ディファレンシャルケース１１には、貫通穴１２の上部に開口する第１の給油通路１３が形成され、また貫通穴１２の下部に開口する第２の排油通路１４が形成されている。外輪２１の上部には、第２の給油通路２１ｃが半径方向に貫通して形成され、外輪２１の下部には、第１の排油通路２１ｄが半径方向に貫通し形成されている。第２の給油通路２１ｃの外径側は第１の給油通路１３に開口し、第１の排油通路２１ｄの外径側は第２の排油通路１４に開口している。ディファレンシャルケース１１の内部空間８１は、リングギヤ８０が回転する作動空間でもあり、潤滑油を貯留する貯留空間でもある。リングギヤ８０によって掻き揚げられた潤滑油は、流れＦに示すように、第１の給油通路１３および第２の給油通路２１ｃを経て外輪２１および内輪２２、３２間に導かれ、また流れＧに示すように、直接外輪２１および内輪２２、３２間に導かれる。外輪２１および内輪２２、３２間内で下方へ落下した潤滑油は、流れＲ１に示すように、第１の排油通路２１ｄおよび第２の排油通路１４を経て内部空間８１へ排出され、また流れＲ２に示すように、外輪２１および内輪２２、３２間から直接内部空間８１へ排出されるようになっている。   As shown in FIG. 1, the differential case 11 is formed with a first oil supply passage 13 that opens at the top of the through hole 12, and a second oil discharge passage 14 that opens at the bottom of the through hole 12. ing. A second oil supply passage 21 c is formed through the upper portion of the outer ring 21 in a radial direction, and a first oil discharge passage 21 d is formed through the lower portion of the outer ring 21 in a radial direction. The outer diameter side of the second oil supply passage 21c opens to the first oil supply passage 13, and the outer diameter side of the first oil discharge passage 21d opens to the second oil discharge passage 14. The internal space 81 of the differential case 11 is a working space in which the ring gear 80 rotates and a storage space for storing lubricating oil. As shown in the flow F, the lubricating oil pumped up by the ring gear 80 is guided between the outer ring 21 and the inner rings 22 and 32 via the first oil supply passage 13 and the second oil supply passage 21c, and is shown in the flow G. Thus, it is guided directly between the outer ring 21 and the inner rings 22 and 32. Lubricating oil dropped downward between the outer ring 21 and the inner rings 22 and 32 is discharged into the internal space 81 through the first oil discharge passage 21d and the second oil discharge passage 14 as shown in the flow R1, and As indicated by the flow R2, the air is discharged directly from the space between the outer ring 21 and the inner rings 22, 32 to the inner space 81.

次に上述した構成にもとづいて、回転軸装置１０の組付け動作を説明する。   Next, the assembly operation of the rotary shaft device 10 will be described based on the above-described configuration.

図１および図２に示すように、ピニオン軸４０の第１の嵌合面４２に転がり軸受２０の内輪２２、３２を嵌合させ、ピニオン軸４０の第１の段部に内輪３２のピニオンギヤ４１側の端面を当接させる。外輪２１の第４の嵌合面２１ｂにオイルシール６０を嵌合固定し、コンパニオンフランジ５０の第３の嵌合面５１にスリンガー７０を嵌合固定する。コンパニオンフランジ５０をネジ部４５に嵌め込み、さらにスプライン４４に嵌め込み、第１のリップ部６４および第２のリップ部６５をコンパニオンフランジ５０の第３の嵌合面５１に摺接させる。内輪２２のピニオンギヤ４１と反対側の端面にコンパクトフランジ５０のピニオンギヤ４１側の端面５３が当接すると同時に、オイルシール６０の第３のリップ部６３がスリンガー７０の側面に当接する。   As shown in FIGS. 1 and 2, the inner rings 22 and 32 of the rolling bearing 20 are fitted to the first fitting surface 42 of the pinion shaft 40, and the pinion gear 41 of the inner ring 32 is fitted to the first step portion of the pinion shaft 40. The end face on the side is brought into contact. The oil seal 60 is fitted and fixed to the fourth fitting surface 21 b of the outer ring 21, and the slinger 70 is fitted and fixed to the third fitting surface 51 of the companion flange 50. The companion flange 50 is fitted into the screw portion 45 and further fitted into the spline 44, and the first lip portion 64 and the second lip portion 65 are brought into sliding contact with the third fitting surface 51 of the companion flange 50. The end surface 53 of the compact flange 50 on the side of the pinion gear 41 abuts against the end surface of the inner ring 22 opposite to the pinion gear 41, and at the same time, the third lip portion 63 of the oil seal 60 abuts on the side surface of the slinger 70.

続いてネジ部４５にワッシャ５６が嵌め込まれ、ネジ部４５にナット５８が螺合される。ナット５８を締め付けると、内輪２２、３２が、ピニオン軸４０の第１の段部およびコンパニオンフランジ５０のピニオンギヤ４１側の端面５３間で挟み込まれ、コンパニオンフランジ５０の回転が、内輪２２、内輪３２へ伝達可能となり、スプライン４４を介してピニオン軸４０へ伝達可能となる。さらにディファレンシャルケース１１の貫通穴１２に転がり軸受２０の外輪２１を嵌合し、第２の給油通路２１ｃが第１の給油通路１３に対応するよう外輪２１を回し、外輪２１のフランジ部が図略のボルト等を介してディファレンシャルケース１１に固定される。こうしてディファレンシャルケース１１にピニオン軸４０が転がり軸受２０を介して回転可能に軸承される。   Subsequently, a washer 56 is fitted into the screw portion 45, and a nut 58 is screwed into the screw portion 45. When the nut 58 is tightened, the inner rings 22 and 32 are sandwiched between the first step portion of the pinion shaft 40 and the end face 53 of the companion flange 50 on the pinion gear 41 side, and the rotation of the companion flange 50 is transferred to the inner ring 22 and the inner ring 32. Transmission is possible, and transmission to the pinion shaft 40 via the spline 44 is possible. Further, the outer ring 21 of the rolling bearing 20 is fitted into the through hole 12 of the differential case 11, the outer ring 21 is turned so that the second oil supply passage 21 c corresponds to the first oil supply passage 13, and the flange portion of the outer ring 21 is not shown. It is fixed to the differential case 11 via a bolt or the like. In this way, the pinion shaft 40 is rotatably supported by the differential case 11 via the rolling bearing 20.

次に、ディファレンシャル装置の動作を説明する。エンジンからの回転動力がコンパニオンフランジ５０に伝達されると、内輪２２、３２に伝達されるとともにスプライン４４を介してピニオン軸４０に伝達され、さらにピニオンギヤ４１を介してリングギヤ８０が回転する。リングギヤ８０が回転すると、潤滑油が掻き揚げられ、流れＦに示すように、第１の給油通路１３および第２の給油通路２１ｃを経て外輪２１および内輪２２、３２間に導かれ、また流れＧに示すように、直接外輪２１および内輪２２、３２間に導かれる。外輪２１および内輪２２、３２間内で下方へ落下した潤滑油は、流れＲ１に示すように、第１の排油通路２１ｄおよび第２の排油通路１４を経て内部空間８１へ排出され、また流れＲ２に示すように、外輪２１および内輪２２、３２間から直接内部空間８１へ排出される。内輪２２の回転により、オイルシール６０の第１のリップ部６４および第２のリップ部６４が、内輪２２の第３の嵌合面５１に対して摺接し、オイルシール６０の第３のリップ部６３が、スリンガー７０の側面に対して摺接する。   Next, the operation of the differential device will be described. When the rotational power from the engine is transmitted to the companion flange 50, it is transmitted to the inner rings 22, 32 and is transmitted to the pinion shaft 40 via the spline 44, and the ring gear 80 is further rotated via the pinion gear 41. When the ring gear 80 rotates, the lubricating oil is lifted up and is guided between the outer ring 21 and the inner rings 22 and 32 via the first oil supply passage 13 and the second oil supply passage 21c as shown in the flow F, and the flow G As shown in FIG. 4, the outer ring 21 and the inner rings 22 and 32 are guided directly. Lubricating oil dropped downward between the outer ring 21 and the inner rings 22 and 32 is discharged into the internal space 81 through the first oil discharge passage 21d and the second oil discharge passage 14 as shown in the flow R1, and As shown in the flow R2, the gas is discharged directly between the outer ring 21 and the inner rings 22, 32 to the inner space 81. Due to the rotation of the inner ring 22, the first lip portion 64 and the second lip portion 64 of the oil seal 60 are brought into sliding contact with the third fitting surface 51 of the inner ring 22, and the third lip portion of the oil seal 60. 63 is in sliding contact with the side surface of the slinger 70.

図２および図３において、流れＦに示すように、第１の給油通路１３および第２の給油通路２１ｃを経て外輪２１および内輪２２、３２間に導かれた潤滑油の一部は、内輪２２の回転による遠心力が作用し、流れＰ１、Ｐ２、Ｐ３に示すように、テーパ面２２ｂ、内輪側軌道面２２ａを経て外輪２１の第１の環状溝に導かれる。さらに、流れＰ４、Ｐ５に示すように、第１の環状溝から落下した潤滑油は、第２の環状溝に導かれ、回転する第２の傾斜面２２ｅによって潤滑油に遠心力が作用し、第２の環状溝に入った潤滑油は、玉２４側へ排出され、外輪２１および内輪２２、３２間内で下方へ落下する。このように、第１のリップ部６４周辺の潤滑油は、第２の環状溝を経て玉２４側へ排出され、流れＰ１、Ｐ２によって常に潤滑油が供給される。供給される潤滑油は、ディファレンシャルケース１１の内部空間８１にて自然冷却されたものであるので、第１のリップ部６４周辺の潤滑油の温度の上昇が抑えられてオイルスラッジの発生が抑えられ、第１のリップ部６４の密封性の低下を防ぐことができる。   2 and 3, a part of the lubricating oil introduced between the outer ring 21 and the inner rings 22 and 32 through the first oil supply passage 13 and the second oil supply passage 21c as shown in the flow F is the inner ring 22. As shown in the flows P1, P2 and P3, the centrifugal force due to the rotation of is guided to the first annular groove of the outer ring 21 through the tapered surface 22b and the inner ring side raceway surface 22a. Furthermore, as shown in flows P4 and P5, the lubricating oil dropped from the first annular groove is guided to the second annular groove, and centrifugal force acts on the lubricating oil by the rotating second inclined surface 22e, The lubricating oil that has entered the second annular groove is discharged toward the ball 24 and falls downward between the outer ring 21 and the inner rings 22, 32. Thus, the lubricating oil around the first lip portion 64 is discharged to the ball 24 side through the second annular groove, and the lubricating oil is always supplied by the flows P1 and P2. Since the supplied lubricating oil is naturally cooled in the internal space 81 of the differential case 11, an increase in the temperature of the lubricating oil around the first lip portion 64 is suppressed, and generation of oil sludge is suppressed. The deterioration of the sealing performance of the first lip portion 64 can be prevented.

本発明はこうした実施形態に何等限定されるものではなく、本発明の要旨を逸脱しない範囲において、種々なる態様で実施し得ることは勿論である。   The present invention is not limited to these embodiments, and can of course be implemented in various modes without departing from the gist of the present invention.

上述した実施形態は、断面直線状の第２の傾斜面２２ｃを形成した。他の実施形態として、第２の環状溝の深さが玉２４に向かって次第に浅くなるものであれば、断面円弧状の第２の傾斜面であっても良い。   In the embodiment described above, the second inclined surface 22c having a linear cross section is formed. As another embodiment, if the depth of the second annular groove becomes gradually shallower toward the ball 24, the second inclined surface having an arc cross section may be used.

上述した実施形態は、転がり軸受２０として一対のアンギュラ玉軸受を適用した。他の実施形態として、転がり軸受２０として一対の円すいころ軸受を適用しても良い。   In the embodiment described above, a pair of angular ball bearings is applied as the rolling bearing 20. As another embodiment, a pair of tapered roller bearings may be applied as the rolling bearing 20.

１１：ディファレンシャルケース（ハウジング）、２０：転がり軸受、２１：外輪、２２：内輪、２２ｅ：第２の傾斜面（傾斜面）、２４：玉（転動体）、３２：内輪、３４：玉（転動体）、４０：ピニオン軸（回転軸）、６０：オイルシール、６４：第１のリップ部（リップ部）、６５：第２のリップ部（リップ部） 11: differential case (housing), 20: rolling bearing, 21: outer ring, 22: inner ring, 22e: second inclined surface (inclined surface), 24: ball (rolling element), 32: inner ring, 34: ball (rolling) (Moving body), 40: pinion shaft (rotary shaft), 60: oil seal, 64: first lip portion (lip portion), 65: second lip portion (lip portion)

Claims (1)

転がり軸受は、リング状の外輪と、この外輪の内周側に配置される内輪と、前記外輪および前記内輪間で転動する転動体とからなり、前記外輪をハウジングに嵌合固定し、前記内輪を前記回転軸に嵌合し、前記外輪の内周にオイルシールを取付け、オイルシールの内周側のリップ部を前記内輪に摺接させた回転軸装置において、
前記転動体および前記リップ部間で前記内輪の外周に潤滑油が貯留する環状溝を形成し、この環状溝は、前記転動体に向かって溝深さが次第に浅くなる傾斜面を有することを特徴とする回転軸装置。 The rolling bearing comprises a ring-shaped outer ring, an inner ring disposed on the inner peripheral side of the outer ring, and a rolling element that rolls between the outer ring and the inner ring, and the outer ring is fitted and fixed to a housing, In the rotary shaft device in which an inner ring is fitted to the rotary shaft, an oil seal is attached to the inner periphery of the outer ring, and the lip portion on the inner peripheral side of the oil seal is in sliding contact with the inner ring,
An annular groove for storing lubricating oil is formed on the outer periphery of the inner ring between the rolling element and the lip portion, and the annular groove has an inclined surface whose groove depth gradually decreases toward the rolling element. Rotating shaft device.
JP2011161449A 2011-07-23 2011-07-23 Rotary shaft device Withdrawn JP2013024354A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013217322A1 (en) * 2013-08-30 2015-03-05 Aktiebolaget Skf Outer ring for a rolling bearing and roller bearing
CN107061510A (en) * 2017-04-26 2017-08-18 柳州市乾阳机电设备有限公司 Bearing seal
US10285183B2 (en) 2014-04-30 2019-05-07 Huawei Technologies Co., Ltd. Signal processing method, apparatus, and system for providing service to multiple user equipments at a same time and in a same frequency

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013217322A1 (en) * 2013-08-30 2015-03-05 Aktiebolaget Skf Outer ring for a rolling bearing and roller bearing
DE102013217322B4 (en) * 2013-08-30 2015-12-24 Aktiebolaget Skf Outer ring for a rolling bearing and roller bearing
US10285183B2 (en) 2014-04-30 2019-05-07 Huawei Technologies Co., Ltd. Signal processing method, apparatus, and system for providing service to multiple user equipments at a same time and in a same frequency
CN107061510A (en) * 2017-04-26 2017-08-18 柳州市乾阳机电设备有限公司 Bearing seal

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