JP2012087823A - Rotating shaft device - Google Patents

Rotating shaft device Download PDF

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Publication number
JP2012087823A
JP2012087823A JP2010232519A JP2010232519A JP2012087823A JP 2012087823 A JP2012087823 A JP 2012087823A JP 2010232519 A JP2010232519 A JP 2010232519A JP 2010232519 A JP2010232519 A JP 2010232519A JP 2012087823 A JP2012087823 A JP 2012087823A
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Prior art keywords
rotating shaft
oil seal
inner ring
ring
casing
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Japanese (ja)
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Yozo Taniguchi
陽三 谷口
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JTEKT Corp
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JTEKT Corp
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Priority to JP2010232519A priority Critical patent/JP2012087823A/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
    • F16C19/02—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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

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

Abstract

PROBLEM TO BE SOLVED: To shorten the axial length of a rotating shaft device (differential device) without impairing the airtightness of an oil seal.SOLUTION: The rotating shaft device bears a rotating shaft 30 rotatably via an angular bearing 20 in a casing 11 and is provided with an oil seal 40 between the rotating shaft 30 and the casing 11, and a lubricating oil in the angular bearing 20 for lubricating the angular bearing 20. In this device, the angular bearing 20 is made up of: an outer ring 23 attached to the casing; inner rings 21, 22 arranged at the inner circumferential side of the outer ring 23 and attached to the rotating shaft 30; rolling elements 24, 26 arranged between the outer ring 23 and the inner rings 21, 22; and retainers 25, 27, which retain the rolling elements 24, 26 rotatably. A shielding part 27e, which projects inward in the radial direction and shields the lubricating oil, is provided on the end surface at the oil seal 40 side of the retainer 27.

Description

本発明は、回転軸をアンギュラ軸受を介して回転可能に支持した回転軸装置に関する。   The present invention relates to a rotating shaft device that rotatably supports a rotating shaft via an angular bearing.

自動車のディファレンシャル装置は、ピニオン軸の回転を、リングギヤ、ディファレンシャルギヤケース、遊星歯車を介して車軸に伝えている。図４（特許文献１）に示すように、前記ピニオン軸１００はケーシング１１０にアンギュラ軸受１２０を介して回転可能に支持され、ピニオン軸１００（回転軸）、アンギュラ軸受１２０、ケーシング１１０の一部から回転軸装置が構成される。   A differential device for an automobile transmits rotation of a pinion shaft to an axle through a ring gear, a differential gear case, and a planetary gear. As shown in FIG. 4 (Patent Document 1), the pinion shaft 100 is rotatably supported by a casing 110 via an angular bearing 120. From the pinion shaft 100 (rotating shaft), the angular bearing 120, and a part of the casing 110. A rotating shaft device is configured.

前記アンギュラ軸受１２０は、ケーシング１１０の取付け穴１１１に嵌合される外輪１２１と、外輪１２１の内周側に軸方向に２列配列された第１の内輪１２２、第２の内輪１２３と、外輪１２１と第１の内輪１２２間に配置された第１の玉１２４と、外輪１２１と第２の内輪１２３間に配置された第２の玉１２５と、第１の玉１２４を回転可能に保持する第１の保持器１２６と、第２の玉１２５を回転可能に保持する第２の保持器１２７とからなっている。   The angular bearing 120 includes an outer ring 121 fitted in the mounting hole 111 of the casing 110, a first inner ring 122, a second inner ring 123 arranged in two rows in the axial direction on the inner peripheral side of the outer ring 121, and an outer ring. The first ball 124 disposed between the 121 and the first inner ring 122, the second ball 125 disposed between the outer ring 121 and the second inner ring 123, and the first ball 124 are rotatably held. It consists of a first holder 126 and a second holder 127 that holds the second ball 125 rotatably.

前記外輪１２１の一端内周にオイルシール１３０が嵌合固定され、オイルシール１３０の内周側に設けられた２つのリップ部１３１、１３２が前記第２の内輪１２３に対して回転可能に摺接している。このオイルシール１３０によって、ケーシング１１０内の潤滑油が外部へ漏れるのを防止している。   An oil seal 130 is fitted and fixed to the inner periphery of one end of the outer ring 121, and the two lip portions 131 and 132 provided on the inner periphery side of the oil seal 130 are slidably contacted with the second inner ring 123. ing. The oil seal 130 prevents the lubricating oil in the casing 110 from leaking outside.

前記ケーシング１１０内の潤滑油は、前記アンギュラ軸受１２０に供給されるようになっている。すなわち、前記リングギヤによって掻き揚げられた潤滑油は、ケーシング１１０の潤滑油溝１１２と、外輪１２１の貫通穴１２１ａを経由して２列の玉１２４、１２５間へ供給され、アンギュラ軸受のポンプ作用によって内輪１２２、１２３の小径側から大径側へ送られる。   Lubricating oil in the casing 110 is supplied to the angular bearing 120. That is, the lubricating oil pumped up by the ring gear is supplied between the two rows of balls 124 and 125 via the lubricating oil groove 112 of the casing 110 and the through hole 121a of the outer ring 121, and is pumped by the angular bearing. The inner rings 122 and 123 are fed from the small diameter side to the large diameter side.

特開２００６−９９３０号公報JP 2006-9930 A

第２の内輪１２３の小径側から大径側へ流れる潤滑油が、前記リップ部１３１、１３２の内周に作用して、リップ部１３１、１３２をピニオン軸１００から離れる方向に浮き上がらせようとするため、オイルシール１３０の気密性が損なわれる。これに対し、第２の玉１２５とオイルシール１３０をより離間させ、前記リップ部１３１、１３２の内周に作用する潤滑油の勢いを弱める方法があるが、この場合、ピニオン軸１００、しいてはディファレンシャル装置の軸方向長さが長くなる課題がある。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、オイルシールの気密性を損なうことなく、回転軸装置（ディファレンシャル装置）の軸方向の長さを短くする。   Lubricating oil flowing from the small diameter side to the large diameter side of the second inner ring 123 acts on the inner periphery of the lip parts 131 and 132 and tries to lift the lip parts 131 and 132 away from the pinion shaft 100. Therefore, the airtightness of the oil seal 130 is impaired. In contrast, there is a method in which the second ball 125 and the oil seal 130 are further separated to weaken the momentum of the lubricating oil acting on the inner periphery of the lip portions 131 and 132. In this case, the pinion shaft 100, Has a problem that the axial length of the differential device becomes long. The present invention has been made to solve the above-described problems, and an object thereof is to shorten the axial length of the rotary shaft device (differential device) without impairing the airtightness of the oil seal.

請求項１に記載の発明は、ケーシングにアンギュラ軸受を介して回転軸を回転可能に軸承し、前記回転軸と前記ケーシング間にオイルシールを設け、アンギュラ軸受内にこれを潤滑する潤滑油を設けた回転軸装置において、前記アンギュラ軸受は、前記ケーシングに取付けられる外輪と、外輪の内周側に配置され、前記回転軸に取付けられる内輪と、外輪と内輪間に配置された転動体と、転動体を回転可能に保持する保持器とからなり、保持器のオイルシール側の端面に半径方向内方へ突出し、前記潤滑油を遮蔽する遮蔽部を設けたものである。   According to the first aspect of the present invention, a rotating shaft is rotatably supported on a casing via an angular bearing, an oil seal is provided between the rotating shaft and the casing, and lubricating oil for lubricating the same is provided in the angular bearing. In the rotating shaft device, the angular bearing includes an outer ring attached to the casing, an inner ring disposed on the inner peripheral side of the outer ring, a rolling element disposed between the outer ring and the inner ring, a rolling element disposed between the outer ring and the inner ring. The cage includes a cage that rotatably holds the moving body, and is provided with a shielding portion that projects inward in the radial direction on the oil seal side end surface of the cage and shields the lubricating oil.

この構成によれば、アンギュラ軸受のポンプ作用によって、内輪の小径側から大径側へ潤滑油が流れ、この潤滑油は保持器の遮蔽部で跳ね返される。これにより、オイルシールに作用する潤滑油の勢いが弱まるので、オイルシールの気密性を保てる。   According to this configuration, the lubricating oil flows from the small-diameter side of the inner ring to the large-diameter side by the pump action of the angular bearing, and this lubricating oil is rebounded by the shielding portion of the cage. Thereby, since the momentum of the lubricating oil acting on the oil seal is weakened, the air tightness of the oil seal can be maintained.

請求項２に記載の発明は、前記アンギュラ軸受は、転動体として玉を使用したアンギュラ玉軸受にしたものである。   According to a second aspect of the present invention, the angular bearing is an angular ball bearing using balls as rolling elements.

この構成によれば、玉はコロと比較してアンギュラ軸受における軸方向寸法が短いので、転動体として玉を用いれば、アンギュラ軸受の軸方向の長さを短く出来る。   According to this configuration, since the ball has a shorter axial dimension in the angular bearing than the roller, the axial length of the angular bearing can be shortened by using the ball as a rolling element.

請求項３に記載の発明は、前記保持器は、リング状の環状部と、この環状部に対してオイルシール側へ延びる柱部を有し、前記環状部と前記柱部に前記玉を転動可能に保持するポケットを形成し、前記柱部のオイルシール側の端面にオイルシール側へ延びる連結部を連結し、この連結部のオイルシール側の端面に前記玉に接触しない位置に円盤状の前記遮蔽部を連結したものである。   According to a third aspect of the present invention, the cage includes a ring-shaped annular portion and a column portion extending toward the oil seal side with respect to the annular portion, and the ball is transferred to the annular portion and the column portion. A pocket is formed to be movable, and a connecting part extending to the oil seal side is connected to the end face of the pillar part on the oil seal side, and the end face on the oil seal side of the connecting part is disc-shaped at a position not contacting the ball. The shielding portions are connected.

この構成によれば、柱部と遮蔽部間にリング状の環状部が無い分だけ、遮蔽部で跳ね返された潤滑油が外輪側へ移動しやすくなり、潤滑油の循環がスムーズになるメリットがある。   According to this configuration, there is no merit that the lubricating oil bounced back by the shielding portion easily moves to the outer ring side as much as there is no ring-shaped annular portion between the pillar portion and the shielding portion, and the circulation of the lubricating oil becomes smooth. is there.

本発明によれば、アンギュラ軸受のポンプ作用によって、内輪の小径側から大径側へ潤滑油が流れ、保持器の遮蔽部で跳ね返される。これにより、オイルシールに作用する潤滑油の勢いが弱まるので、オイルシールの気密性を保てる。   According to the present invention, the lubricating oil flows from the small-diameter side of the inner ring to the large-diameter side by the pumping action of the angular bearing, and is rebounded by the shielding portion of the cage. Thereby, since the momentum of the lubricating oil acting on the oil seal is weakened, the air tightness of the oil seal can be maintained.

本発明の実施形態におけるディファレンシャル装置の縦断面図The longitudinal cross-sectional view of the differential apparatus in embodiment of this invention 本発明の実施形態におけるディファレンシャル装置の回転軸装置の縦断面図The longitudinal cross-sectional view of the rotating shaft apparatus of the differential apparatus in embodiment of this invention 本発明の実施形態における回転軸装置の保持器の外観図1 is an external view of a cage of a rotary shaft device according to an embodiment of the present invention. 従来の回転軸装置の縦断面図Longitudinal sectional view of a conventional rotary shaft device

本発明の回転軸装置を自動車のディファレンシャル装置に用いた実施形態を、図１乃至図３にもとづいて説明する。図１は、ディファレンシャル装置の縦断面図、図２は、ディファレンシャル装置の回転軸装置の縦断面図、図３は、回転軸装置の保持器の外観図である。   An embodiment in which the rotary shaft device of the present invention is used in a differential device for an automobile will be described with reference to FIGS. 1 is a longitudinal sectional view of a differential device, FIG. 2 is a longitudinal sectional view of a rotating shaft device of the differential device, and FIG. 3 is an external view of a cage of the rotating shaft device.

図１において、自動車のディファレンシャル装置１０は、ケーシング１１を有し、このケーシング１１にリングギヤ１２が回転可能に軸支されている。また、ケージング１１にアンギュラ玉軸受２０を介してピニオン軸３０が回転可能に軸支されている。前記リングギヤ１２の回転軸線とピニオン軸３０の回転軸線は、互いに上下方向にずれ、直交している。   In FIG. 1, a differential apparatus 10 for an automobile has a casing 11, and a ring gear 12 is rotatably supported by the casing 11. Further, a pinion shaft 30 is rotatably supported on the casing 11 via an angular ball bearing 20. The rotation axis of the ring gear 12 and the rotation axis of the pinion shaft 30 are perpendicular to each other in the vertical direction.

ピニオン軸３０の一端には、リングギヤ１２と噛合うピニオンギヤ３０ａが形成され、ピニオン軸２１の他端には、フランジ継手３１が固定されている。ピニオン軸３０のピニオンギヤ３０ａとフランジ継手３１間には、小径部３０ｂが形成され、この小径部３０ｂにアンギュラ玉軸受２０の第１の内輪２１と第２の内輪２２が嵌合されている。ケーシンング１１には、ピニオン軸３０と同軸に取付け穴１１ａが形成され、この取付け穴１１ａにアンギュラ玉軸受２０の外輪２３が嵌合されている。外輪２３と第１の内輪２１間には、複数の第１の玉２４が転動可能に配置され、これら第１の玉２４は円周方向に等間隔に配置されるよう第１の保持器２５に転動可能に保持されている。外輪２３と第２の内輪２２間には、複数の第２の玉２６が転動可能に配置され、これら第２の玉２６は円周方向に等間隔に配置されるよう第２の保持器２７に転動可能に保持されている。   A pinion gear 30 a that meshes with the ring gear 12 is formed at one end of the pinion shaft 30, and a flange joint 31 is fixed to the other end of the pinion shaft 21. A small diameter portion 30b is formed between the pinion gear 30a of the pinion shaft 30 and the flange joint 31, and the first inner ring 21 and the second inner ring 22 of the angular ball bearing 20 are fitted into the small diameter portion 30b. The casing 11 is formed with a mounting hole 11a coaxially with the pinion shaft 30, and the outer ring 23 of the angular ball bearing 20 is fitted into the mounting hole 11a. A plurality of first balls 24 are arranged between the outer ring 23 and the first inner ring 21 so as to be able to roll, and the first cage 24 is arranged at equal intervals in the circumferential direction. It is hold | maintained at 25 so that rolling is possible. A plurality of second balls 26 are arranged between the outer ring 23 and the second inner ring 22 so as to be able to roll, and the second cage 26 is arranged such that these second balls 26 are arranged at equal intervals in the circumferential direction. 27 is held so as to be able to roll.

前記ピニオン軸３０、フランジ継手３１、アンギュラ玉軸受２０、ケーシング１１の一部によって、回転軸装置が構成される。   The pinion shaft 30, the flange joint 31, the angular ball bearing 20, and a part of the casing 11 constitute a rotating shaft device.

前記第１の内輪２１の内周面には、第１の内輪側転動面２１ａが形成され、前記第２の内輪２２の内周面には、第２の内輪側転動面２２ａが形成されている。前記外輪２３の外周面には、互いに軸方向に離間して第１の外輪側転動面２３ａと第２の外輪側転動面２３ｂが形成され、第１の外輪側転動面２３ａと第２の外輪側転動面２３ｂは、第１の内輪側転動面２１ａと第２の内輪側転動面２２ａよりも内側に形成されている。前記第１の玉２４は、第１の内輪側転動面２１ａと第１の外輪側転動面２３ａ上を転動し、前記第２の玉２６は、第２の内輪側転動面２２ａと第２の外輪側転動面２３ｂ上を転動するようになっている。   A first inner ring-side rolling surface 21 a is formed on the inner peripheral surface of the first inner ring 21, and a second inner ring-side rolling surface 22 a is formed on the inner peripheral surface of the second inner ring 22. Has been. A first outer ring side rolling surface 23b and a second outer ring side rolling surface 23b are formed on the outer circumferential surface of the outer ring 23 so as to be spaced apart from each other in the axial direction. The second outer ring-side rolling surface 23b is formed inside the first inner ring-side rolling surface 21a and the second inner ring-side rolling surface 22a. The first ball 24 rolls on the first inner ring-side rolling surface 21a and the first outer ring-side rolling surface 23a, and the second ball 26 has the second inner ring-side rolling surface 22a. And on the second outer ring-side rolling surface 23b.

図２に示すように、第１の内輪２１を支持するときにかかる力の方向ｍが半径方向外方に向かって第２の内輪２２側へ傾斜し、第２の内輪２２を支持するときにかかる力の方向ｎが半径方向外方に向かって第１の内輪２１側へ傾斜している。前記２つの力の方向ｍ、ｎ、すなわち２つのアキシャル方向によって、ピニオン軸２１はラジアル方向並びにスラスト方向に支持されるようになっている。   As shown in FIG. 2, when the direction m of the force applied when supporting the first inner ring 21 is inclined outwardly in the radial direction toward the second inner ring 22, and when supporting the second inner ring 22. The direction n of the force is inclined toward the first inner ring 21 toward the outer side in the radial direction. The pinion shaft 21 is supported in the radial direction and the thrust direction by the two force directions m and n, that is, the two axial directions.

前記第１の保持器２５は、リング状の第２の保持器側環状部２５ａと、軸方向に延びる柱部２５ｂとからなる冠型保持器である。前記第２の保持器２７は、リング状の第１の保持器側環状部２７ａと、軸方向に延びる柱部２７ｂとからなる冠型保持器である。柱部２５ｂ、２７ｂは、円周方向に等間隔に設けられ、第２の保持器側環状部２５ａと柱部２５ｂとで第１の玉２４を転動可能に保持する第１のポケット２５ｃが形成され、第１の保持器側環状部２７ａと柱部２７ｂとで第２の玉２６を転動可能に保持する第２のポケット２７ｃが形成されている。前記第１の保持器２５と前記第２の保持器２７は、後述する連結部２７ｄと遮蔽部２７ｅの有無を除き、同一の構成である。   The first cage 25 is a crown type cage composed of a ring-shaped second cage-side annular portion 25a and a column portion 25b extending in the axial direction. The second cage 27 is a crown type cage composed of a ring-shaped first cage-side annular portion 27a and a column portion 27b extending in the axial direction. The column portions 25b and 27b are provided at equal intervals in the circumferential direction, and a first pocket 25c that holds the first ball 24 in a rollable manner by the second cage-side annular portion 25a and the column portion 25b is provided. A second pocket 27c is formed to hold the second ball 26 in a rollable manner by the first cage-side annular portion 27a and the column portion 27b. The first cage 25 and the second cage 27 have the same configuration except for the presence or absence of a connecting portion 27d and a shielding portion 27e described later.

図３に示すように、前記第２の保持器２７は、さらに２つ置きの柱部２７ｂの端面に一端面が連結されピニオンギヤ３０ａと反対側へ延びる連結部２７ｄと、連結部２７ｄの他端面に連結された円盤状の遮蔽部２７ｅを有する。遮蔽部２７ｅは、連結部２７ｄに対して半径方向外方並びに半径方向内方へ突出している。遮蔽部２７ｅの半径方向内方側は、第２の内輪２２の外周面近傍まで延びている。   As shown in FIG. 3, the second retainer 27 includes a connecting portion 27d having one end surface connected to the end surface of every two column portions 27b and extending to the opposite side of the pinion gear 30a, and the other end surface of the connecting portion 27d. And a disk-shaped shielding portion 27e connected to each other. The shielding part 27e protrudes radially outward and radially inward with respect to the connecting part 27d. The radially inner side of the shield 27 e extends to the vicinity of the outer peripheral surface of the second inner ring 22.

図２に示すように、前記外輪２３のフランジ継手３１側の内周面には、オイルシール４０が嵌合固定されている。オイルシール４０は、金属環４１、ゴム部４２、リング状のバンド４２とからなっている。ゴム部４２は、３つのリップ部４２ａ、４２ｂ、４２ｃを有する。第１のリップ部４２ａと第２のリップ部４２ｂは、第２の内輪２２の外周面に回転可能に摺接し、第３のリップ部４２ｃは、フランジ継手３１の外周面に嵌合固定されたプロテクタ５０の側面に回転可能に摺接する。第１のリップ部４２ａのみが前記バンド４２によって半径方向内方へ押付けられるようになっている。   As shown in FIG. 2, an oil seal 40 is fitted and fixed to the inner peripheral surface of the outer ring 23 on the flange joint 31 side. The oil seal 40 includes a metal ring 41, a rubber part 42, and a ring-shaped band 42. The rubber part 42 has three lip parts 42a, 42b and 42c. The first lip portion 42 a and the second lip portion 42 b are slidably contacted with the outer peripheral surface of the second inner ring 22, and the third lip portion 42 c is fitted and fixed to the outer peripheral surface of the flange joint 31. The sliding contact with the side surface of the protector 50 is possible. Only the first lip portion 42 a is pressed radially inward by the band 42.

前記ケーシング１１には、取付け穴１１ａの上部に開口する油導入溝１１ｂが形成され、油導入溝１１ｂの一端はケーシング１１内部の空間１１ｃに開口している。空間１１ｃは、リングギヤ１２の回転を許容するとともに、潤滑油を貯留する役目を持っている。潤滑油は、リングギヤ１２の下からリングギヤ１２の直径の４分の１の深さまで入っている。またケーシング１１には、取付け穴１１ａの下部に開口する油戻り溝１１ｄが形成され、油戻り溝１１ｄの一端はケーシング１１内部の空間１１ｃに開口している。   The casing 11 is formed with an oil introduction groove 11b that opens at the top of the mounting hole 11a, and one end of the oil introduction groove 11b opens into a space 11c inside the casing 11. The space 11c has a role of allowing the ring gear 12 to rotate and storing lubricating oil. Lubricating oil enters from the bottom of the ring gear 12 to a depth that is a quarter of the diameter of the ring gear 12. The casing 11 is formed with an oil return groove 11d that opens at a lower portion of the mounting hole 11a, and one end of the oil return groove 11d opens into a space 11c inside the casing 11.

前記外輪２３には、前記油導入溝１１ｂと対応する位置に半径方向に貫通するパス穴２３ｃが形成されている。パス穴２３ｃの内径側は、ピニオン軸３０の軸方向において、第１の内輪２１と第２の内輪２２間に対応する位置に開口している。また外輪２３には、前記油戻り溝１１ｄと対応する位置に貫通するパス穴２３ｄが形成されている。パス穴２３ｄの内径側は、ピニオン軸３０の軸方向において、連結部２７ｄに対応する位置に開口している。   The outer ring 23 is formed with a pass hole 23c penetrating in the radial direction at a position corresponding to the oil introduction groove 11b. An inner diameter side of the pass hole 23 c opens at a position corresponding to the space between the first inner ring 21 and the second inner ring 22 in the axial direction of the pinion shaft 30. Further, the outer ring 23 is formed with a pass hole 23d penetrating at a position corresponding to the oil return groove 11d. An inner diameter side of the pass hole 23d is opened at a position corresponding to the connecting portion 27d in the axial direction of the pinion shaft 30.

次に上述した構成にもとづいて、動作を説明する。   Next, the operation will be described based on the above-described configuration.

ピニオン軸３０が回転すると、これに噛合するリングギヤ１２も回転する。リングギヤ１２の回転は、さらに図略のディファレンシャルギヤケース、遊星歯車を介して車軸に伝えられる。   When the pinion shaft 30 rotates, the ring gear 12 that meshes with the pinion shaft 30 also rotates. The rotation of the ring gear 12 is further transmitted to the axle via an unillustrated differential gear case and a planetary gear.

ケーシング１１内部の空間１１ｃには、潤滑油がリングギヤ１２の下からリングギヤの直径の４分の１の深さまで入っている。リングギヤ１２の回転によって、貯留された潤滑油が掻き揚げられ、油導入溝１１ｂに導かれる。さらに、パス穴２３ｃを通って、第１の内輪２１と第２の内輪２２間に導かれる。ピニオン軸３０の回転によって、第１の内輪２１と第２の内輪２２がピニオン軸３０と同方向に同量回転し、第１の玉２４と第２の玉２６が公転しながらピニオン軸３０と同方向に回転する。また、第１の保持器２５と第２の保持器２７がピニオン軸３０と同方向に回転する。この結果、アンギュラ玉軸受２０自体のポンプ作用により、第１の内輪２１において、小径側から大径側へ潤滑油が流れ、ケーシング１１内部の空間１１ｃへ導かれる。また、アンギュラ玉軸受２０自体のポンプ作用により、第２の内輪２２において、小径側から大径側へ潤滑油が流れ、第２の保持器２７の遮蔽部２７ｅで跳ね返される。跳ね返された潤滑油は、外輪２３の第２の外輪側転動面２３ｂに沿って第１の内輪２１と第２の内輪２２間へ戻されるか、あるいは、パス穴２３ｄ、油戻り溝１１ｄを経てケーシング１１内部の空間１１ｃへ戻される。   Lubricating oil enters the space 11c inside the casing 11 from the bottom of the ring gear 12 to a depth that is a quarter of the diameter of the ring gear. Due to the rotation of the ring gear 12, the stored lubricating oil is lifted and guided to the oil introduction groove 11b. Further, it is guided between the first inner ring 21 and the second inner ring 22 through the pass hole 23c. The rotation of the pinion shaft 30 causes the first inner ring 21 and the second inner ring 22 to rotate by the same amount in the same direction as the pinion shaft 30, while the first ball 24 and the second ball 26 revolve around the pinion shaft 30. Rotate in the same direction. Further, the first retainer 25 and the second retainer 27 rotate in the same direction as the pinion shaft 30. As a result, the lubricating oil flows from the small diameter side to the large diameter side in the first inner ring 21 by the pump action of the angular ball bearing 20 itself, and is guided to the space 11 c inside the casing 11. Further, due to the pumping action of the angular ball bearing 20 itself, the lubricating oil flows from the small diameter side to the large diameter side in the second inner ring 22 and is rebounded by the shielding portion 27e of the second cage 27. The rebounded lubricating oil is returned between the first inner ring 21 and the second inner ring 22 along the second outer ring-side rolling surface 23b of the outer ring 23, or passes through the pass hole 23d and the oil return groove 11d. After that, it is returned to the space 11 c inside the casing 11.

第２の内輪２２の第２の内輪側転動面２２ａに沿って潤滑油が、第２の内輪２２の小径側から大径側へ流れるときに、第２の保持器２７の遮蔽部２７ｅで潤滑油が跳ね返され、オイルシール４０の第１のリップ部４２ａの内周面に作用する潤滑油の流速を小さくするとともに流量を減らしているので、オイルシール４０から外部へ潤滑油の漏れが無くなる。遮蔽部２７ｅで跳ね返された潤滑油が、外輪２３側へ流れるときに、遮るものは、連結部２７ｄしかないためスムーズに流れる。   When the lubricating oil flows along the second inner ring side rolling surface 22a of the second inner ring 22 from the small diameter side to the large diameter side of the second inner ring 22, the shielding portion 27e of the second cage 27 Since the lubricating oil is rebounded and the flow velocity of the lubricating oil acting on the inner peripheral surface of the first lip portion 42a of the oil seal 40 is reduced and the flow rate is reduced, the leakage of the lubricating oil from the oil seal 40 to the outside is eliminated. . When the lubricating oil bounced off by the shielding part 27e flows to the outer ring 23 side, the lubricating oil flows smoothly because there is only the connecting part 27d.

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、アンギュラ軸受として、アンギュラ玉軸受２０を使用した例について述べたが、円すいころ軸受を使用しても良い。この場合、アンギュラ玉軸受２０の第１の玉２４を第１の円すいころに置き換え、第２の玉２６を第２の円すいころに置き換え、第１の円すいころと第２の円すいころの小径側が内側に、第１の円すいころと第２の円すいころの大径側が外側になるように配置する。アンギュラ玉軸受２０から円すいころ軸受に変更することにより、軸方向長さが長くなる反面、ラジアル荷重、スラスト荷重を高めることが出来る。   In the above-described embodiment, an example in which the angular ball bearing 20 is used as the angular bearing has been described. However, a tapered roller bearing may be used. In this case, the first ball 24 of the angular ball bearing 20 is replaced with a first tapered roller, the second ball 26 is replaced with a second tapered roller, and the small diameter side of the first tapered roller and the second tapered roller is On the inner side, the first tapered roller and the second tapered roller are arranged so that the large diameter side is on the outer side. By changing from the angular ball bearing 20 to the tapered roller bearing, the axial length is increased, but the radial load and the thrust load can be increased.

さらに上述した実施形態は、第２の保持器２７として、リング状の第１の保持器側環状部２７ａと、軸方向に延びる柱部２７ｂとからなる冠型保持器について説明したが、軸方向にずらしてリング状の第１の保持器側環状部とリング状のオイルシール側環状部を配置し、第１の保持器側環状部とオイルシール側環状部を円周方向に複数配置した柱部２７ｂで繋いだ保持器を使用しても良い。この場合、オイルシール側環状部に連結部の一端を連結し、連結部の他端に遮蔽部を連結する。   Furthermore, although embodiment mentioned above demonstrated the crown type holder | retainer which consists of the ring-shaped 1st retainer side annular part 27a and the pillar part 27b extended in an axial direction as the 2nd retainer 27, it is axial direction. A ring in which a ring-shaped first cage-side annular portion and a ring-shaped oil seal-side annular portion are arranged, and a plurality of the first cage-side annular portion and the oil seal-side annular portion are arranged in the circumferential direction. A cage connected by the portion 27b may be used. In this case, one end of the connecting portion is connected to the oil seal side annular portion, and the shielding portion is connected to the other end of the connecting portion.

またさらに上述した実施形態は、外輪２３と第２の内輪２２をフランジ継手３１側へ軸方向に延ばし、オイルシール４０をアンギュラ玉軸受２０の外輪２３に嵌合固定したが、オイルシール４０と遮蔽部２７ｅ間で外輪２３と第２の内輪２２を軸方向に分割しても良い。   Further, in the above-described embodiment, the outer ring 23 and the second inner ring 22 are extended in the axial direction toward the flange joint 31 and the oil seal 40 is fitted and fixed to the outer ring 23 of the angular ball bearing 20. The outer ring 23 and the second inner ring 22 may be divided in the axial direction between the portions 27e.

上述した実施形態は、回転軸としてディファレンシャル装置１０のピニオン軸３０を適用した例について述べたが、回転軸として工作機械の横型マシニングセンタの主軸を適用しても良い。   In the above-described embodiment, the example in which the pinion shaft 30 of the differential device 10 is applied as the rotation axis is described. However, the main shaft of a horizontal machining center of a machine tool may be applied as the rotation axis.

さらに上述した実施形態は、回転軸としてディファレンシャル装置１０のピニオン軸３０を適用した例について述べたが、回転軸として自動車のトランスファー装置のピニオン軸を適用しても良い。 Furthermore, although embodiment mentioned above described the example which applied the pinion shaft 30 of the differential apparatus 10 as a rotating shaft, you may apply the pinion shaft of the transfer apparatus of a motor vehicle as a rotating shaft.

１１：ケーシング、２０：アンギュラ玉軸受（アンギュラ軸受）、２１：第１の内輪（内輪）、２２：第２の内輪（内輪）、２３：外輪、２４：第１の玉（転動体）、２５：第１の保持器（保持器）、２６：第２の玉（転動体）、２７：第２の保持器（保持器）、２７ａ：第１の保持器側環状部（環状部）、２７ｂ：柱部、２７ｅ：遮蔽部、３０：ピニオン軸（回転軸）、４０：オイルシール   11: casing, 20: angular ball bearing (angular bearing), 21: first inner ring (inner ring), 22: second inner ring (inner ring), 23: outer ring, 24: first ball (rolling element), 25 : First retainer (retainer), 26: second ball (rolling element), 27: second retainer (retainer), 27a: first retainer side annular portion (annular portion), 27b : Pillar part, 27e: shielding part, 30: pinion shaft (rotating shaft), 40: oil seal

Claims (3)

ケーシングにアンギュラ軸受を介して回転軸を回転可能に軸承し、前記回転軸と前記ケーシング間にオイルシールを設け、アンギュラ軸受内にこれを潤滑する潤滑油を設けた回転軸装置において、
前記アンギュラ軸受は、前記ケーシングに取付けられる外輪と、外輪の内周側に配置され、前記回転軸に取付けられる内輪と、外輪と内輪間に配置された転動体と、転動体を回転可能に保持する保持器とからなり、保持器のオイルシール側の端面に半径方向内方へ突出し、前記潤滑油を遮蔽する遮蔽部を設けたことを特徴とする回転軸装置。 In a rotary shaft device in which a rotary shaft is rotatably supported on a casing via an angular bearing, an oil seal is provided between the rotary shaft and the casing, and a lubricating oil is provided in the angular bearing to lubricate the rotary shaft device.
The angular bearing includes an outer ring attached to the casing, an inner ring disposed on the inner peripheral side of the outer ring, an inner ring attached to the rotating shaft, a rolling element disposed between the outer ring and the inner ring, and a rolling element held rotatably. A rotary shaft device comprising: a retainer configured to project a radially inwardly projecting end surface on an oil seal side of the retainer to shield the lubricating oil. 前記アンギュラ軸受は、転動体として玉を使用したアンギュラ玉軸受であることを特徴とする請求項１に記載の回転軸装置。 The rotary shaft device according to claim 1, wherein the angular bearing is an angular ball bearing using balls as rolling elements. 前記保持器は、リング状の環状部と、この環状部に対してオイルシール側へ延びる柱部を有し、前記環状部と前記柱部に前記玉を転動可能に保持するポケットを形成し、前記柱部のオイルシール側の端面にオイルシール側へ延びる連結部を連結し、この連結部のオイルシール側の端面に前記玉に接触しない位置に円盤状の前記遮蔽部を連結したことを特徴とする請求項２に記載の回転軸装置。 The retainer includes a ring-shaped annular portion and a column portion extending toward the oil seal side with respect to the annular portion, and a pocket is formed in the annular portion and the column portion to hold the ball in a rollable manner. The connecting portion extending to the oil seal side is connected to the end surface of the pillar portion on the oil seal side, and the disc-shaped shielding portion is connected to the oil seal side end surface of the connecting portion at a position not contacting the ball. The rotating shaft device according to claim 2, wherein the rotating shaft device is a rotating shaft device.
JP2010232519A 2010-10-15 2010-10-15 Rotating shaft device Pending JP2012087823A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018029923A1 (en) * 2016-08-10 2018-02-15 本田技研工業株式会社 Transfer device and power transmission device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018029923A1 (en) * 2016-08-10 2018-02-15 本田技研工業株式会社 Transfer device and power transmission device
US10767752B2 (en) 2016-08-10 2020-09-08 Honda Motor Co., Ltd. Transfer device and power transmission device

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