JP3724506B2 - One-way clutch built-in pulley device - Google Patents

One-way clutch built-in pulley device Download PDF

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JP3724506B2
JP3724506B2 JP2005139604A JP2005139604A JP3724506B2 JP 3724506 B2 JP3724506 B2 JP 3724506B2 JP 2005139604 A JP2005139604 A JP 2005139604A JP 2005139604 A JP2005139604 A JP 2005139604A JP 3724506 B2 JP3724506 B2 JP 3724506B2
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Prior art keywords
pulley
peripheral surface
sleeve
way clutch
outer peripheral
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JP2005265193A (en
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健夫 大熊
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—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
    • F16C33/7896—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members with two or more discrete sealings arranged in series
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16C2361/63—Gears with belts and pulleys
    • 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
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F16C33/7856—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race with a single sealing lip
    • 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
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pulleys (AREA)
  • Sealing Of Bearings (AREA)

Description

本発明の一方向クラッチ内蔵型プーリ装置は、例えば自動車用の発電機であるオルタネータの回転軸の端部に固定し、エンジンのクランクシャフトの端部に固定した駆動プーリとの間に無端ベルトを掛け渡す事により、上記オルタネータを駆動する為に利用する。   The pulley device with a built-in one-way clutch of the present invention is, for example, an endless belt that is fixed to an end of a rotating shaft of an alternator that is a generator for an automobile, and a drive pulley that is fixed to an end of an engine crankshaft. It is used to drive the alternator by passing it over.

自動車の走行用エンジンを駆動源として、自動車に必要な発電を行なうオルタネータの構造が、例えば特許文献１に記載されている。図６は、この特許文献１に記載されたオルタネータ１を示している。ハウジング２の内側に回転軸３を、１対の転がり軸受４、４により、回転自在に支持している。この回転軸３の中間部には、ロータ５と整流子６とを設けている。又、この回転軸３の一端部（図６の右端部）で上記ハウジング２外に突出した部分には、プーリ７を固定している。エンジンへの組み付け状態では、このプーリ７に無端ベルトを掛け渡し、エンジンのクランクシャフトにより、上記回転軸３を回転駆動自在とする。   For example, Patent Document 1 discloses a structure of an alternator that generates power necessary for an automobile by using an automobile traveling engine as a drive source. FIG. 6 shows an alternator 1 described in Patent Document 1. A rotating shaft 3 is rotatably supported by a pair of rolling bearings 4 and 4 inside the housing 2. A rotor 5 and a commutator 6 are provided at an intermediate portion of the rotating shaft 3. Further, a pulley 7 is fixed to a portion protruding from the housing 2 at one end portion (right end portion in FIG. 6) of the rotating shaft 3. In an assembled state to the engine, an endless belt is stretched over the pulley 7 so that the rotary shaft 3 can be driven to rotate by the crankshaft of the engine.

上記プーリ７として従来一般的には、単に上記回転軸３に固定しただけのものを使用していた。これに対して近年、無端ベルトの走行速度が一定若しくは上昇傾向にある場合には、無端ベルトから回転軸への動力の伝達を自在とし、無端ベルトの走行速度が低下傾向にある場合には、プーリと回転軸との相対回転を自在とする、一方向クラッチ内蔵型プーリ装置が各種提案され、一部で使用されている。例えば、特許文献２〜８等に、上述の様な機能を有する一方向クラッチ内蔵型プーリ装置が記載されている。又、一部ではこの様な一方向クラッチ内蔵型プーリ装置が、実際に使用されている。   Conventionally, as the pulley 7, a pulley that is simply fixed to the rotating shaft 3 has been used. On the other hand, in recent years, when the traveling speed of the endless belt is constant or increasing, it is possible to freely transmit power from the endless belt to the rotating shaft, and when the traveling speed of the endless belt is decreasing, Various one-way clutch built-in pulley devices that allow relative rotation between the pulley and the rotating shaft have been proposed and used in part. For example, Patent Documents 2 to 8 describe a one-way clutch built-in pulley device having the above-described function. Also, in some cases, such a one-way clutch built-in pulley apparatus is actually used.

図７は、このうちの特許文献６に記載されている一方向クラッチ内蔵型プーリ装置を示している。この一方向クラッチ内蔵型プーリ装置は、オルタネータ１（図６）等の回転軸３の先端部にボルト８により結合固定自在なスリーブ９を有する。そして、このスリーブ９の周囲にプーリ７ａを、このスリーブ９と同心に配置している。そして、これらスリーブ９の外周面とプーリ７ａの内周面との間に、１対のサポート軸受１０、１０と一方向クラッチ１１とを設けている。このうちのサポート軸受１０、１０は、上記プーリ７ａに加わるラジアル荷重を支承しつつ、上記スリーブ９とプーリ７ａとの相対回転を自在とする。又、上記一方向クラッチ１１は、上記プーリ７ａが上記スリーブ９に対して所定方向に相対回転する傾向となる場合にのみ、このプーリ７ａから上記スリーブ９への回転力の伝達を自在とする。   FIG. 7 shows the one-way clutch built-in pulley apparatus described in Patent Document 6 among them. This one-way clutch built-in pulley apparatus has a sleeve 9 that can be coupled and fixed by a bolt 8 at the tip of a rotating shaft 3 such as an alternator 1 (FIG. 6). A pulley 7 a is arranged around the sleeve 9 so as to be concentric with the sleeve 9. A pair of support bearings 10 and 10 and a one-way clutch 11 are provided between the outer peripheral surface of the sleeve 9 and the inner peripheral surface of the pulley 7a. Of these, the support bearings 10 and 10 support the radial load applied to the pulley 7a, while allowing relative rotation between the sleeve 9 and the pulley 7a. Further, the one-way clutch 11 can freely transmit the rotational force from the pulley 7a to the sleeve 9 only when the pulley 7a tends to rotate relative to the sleeve 9 in a predetermined direction.

上記一方向クラッチ１１を構成し、上記プーリ７ａの軸方向中間部に内嵌固定した一方向クラッチ用外輪１２の内周面には、ランプ部と呼ばれる複数の凹部１３を、円周方向に亙って等間隔に形成し、上記内周面をカム面１４としている。これに対して、上記一方向クラッチ１１を構成する、上記スリーブ９の軸方向中間部に外嵌固定した一方向クラッチ用内輪１５の外周面は、ほぼ軸方向全長に亙り単なる円筒面としている。又、これら一方向クラッチ用外輪１２及び一方向クラッチ用内輪１５と共に上記一方向クラッチ１１を構成する複数個のローラ１６は、上記一方向クラッチ用外輪１２と共に回転するクラッチ用保持器１７に、転動及び円周方向に亙る若干の変位自在に支持している。そして、このクラッチ用保持器１７に設けた柱部と上記各ローラ１６との間にばねを設けている。これら各ばねは上記各ローラ１６を、上記カム面１４の内周面と上記一方向クラッチ用内輪１５の外周面との間に形成される円筒状隙間の寸法のうち、直径方向に関する幅が狭くなった部分に向け、弾性的に押圧している。 On the inner peripheral surface of the outer ring 12 for a one-way clutch that constitutes the one-way clutch 11 and is fitted and fixed to the intermediate portion in the axial direction of the pulley 7a, a plurality of recesses 13 called ramp portions are provided in the circumferential direction. Thus, the inner peripheral surface is used as the cam surface 14. On the other hand, the outer peripheral surface of the inner ring 15 for a one-way clutch that is externally fitted and fixed to the intermediate portion in the axial direction of the sleeve 9 constituting the one-way clutch 11 is a simple cylindrical surface over almost the entire length in the axial direction. A plurality of rollers 16 constituting the one-way clutch 11 together with the one-way clutch outer ring 12 and the one-way clutch inner ring 15 are transferred to a clutch holder 17 that rotates together with the one-way clutch outer ring 12. It is supported so as to be able to move and move slightly in the circumferential direction. A spring is provided between the column portion provided in the clutch retainer 17 and each roller 16. Each of these springs is the rollers 16, of the dimension of the cylindrical gap formed between the inner and outer circumferential surfaces of the one-way clutch inner race 15 of the cam surface 14, narrower about the diametrical direction It is elastically pressed toward the part.

一方、上記プーリ７ａの軸方向両端寄り部分内周面と上記スリーブ９の軸方向両端寄り部分外周面とに、それぞれが前記各サポート軸受１０、１０を構成する、外輪１８及び内輪１９を嵌合固定している。そして、上記外輪１８の内周面に形成した外輪軌道２０と、上記内輪１９の外周面に形成した内輪軌道２１との間に、複数の玉２２を転動自在に設けている。又、上記プーリ７ａ及びスリーブ９の軸方向両端側に存在する、上記各外輪１８の端部内周面と上記各内輪１９の端部外周面との間に、それぞれシールリング２３、２３を設け、上記各サポート軸受１０、１０及び一方向クラッチ１１の内部空間を密封している。一方、上記スリーブ９の前記回転軸３と反対側の端部の外周面に環状部材２４を、この端部側に設けたサポート軸受１０と対向させる状態で外嵌固定している。   On the other hand, the outer ring 18 and the inner ring 19 that constitute the support bearings 10 and 10, respectively, are fitted to the inner peripheral surface of the pulley 7a near the both ends in the axial direction and the outer peripheral surface of the sleeve 9 near the both ends in the axial direction. It is fixed. A plurality of balls 22 are provided so as to roll between an outer ring raceway 20 formed on the inner peripheral surface of the outer ring 18 and an inner ring raceway 21 formed on the outer peripheral surface of the inner ring 19. Also, seal rings 23 and 23 are provided between the inner peripheral surface of the end of each outer ring 18 and the outer peripheral surface of the end of each inner ring 19 that are present on both axial ends of the pulley 7a and the sleeve 9, respectively. The internal spaces of the support bearings 10 and 10 and the one-way clutch 11 are sealed. On the other hand, an annular member 24 is fitted and fixed to the outer peripheral surface of the end portion of the sleeve 9 opposite to the rotary shaft 3 so as to face the support bearing 10 provided on the end portion side.

上述の様な一方向クラッチ内蔵型プーリ装置を使用する理由は、次の通りである。前記走行用エンジンのクランクシャフトには爆発に同期した回転速度の変動があるが、この走行用エンジンがディーゼルエンジン或は直噴式のガソリンエンジンであった場合、アイドリング時等、低回転時にはクランクシャフトの回転角速度の変動が特に大きくなる。この結果、上記クランクシャフトの端部に固定した駆動プーリに掛け渡した無端ベルト２５の走行速度も細かく変動する事になる。一方、この無端ベルト２５によりプーリ７ａを介して回転駆動されるオルタネータ１の回転軸３は、この回転軸３並びにこの回転軸３に固定したロータ５及び整流子６（図６）等の慣性質量に基づき、それ程急激には変動しない。従って、上記プーリ７ａを回転軸３に対し単に固定しただけの場合には、ベルトの走行速度低下時に上記回転軸３の回転速度がそのまま低下し、オルタネータ１の発電効率が低下する。同時に、クランクシャフトの回転角速度の変動に伴い、上記無端ベルト２５とプーリ７ａとが両方向に擦れ合う傾向となる。この結果、このプーリ７ａと擦れ合う無端ベルトに、繰り返し異なる方向の応力が作用して、この無端ベルト２５とプーリ７ａとの間に滑りが発生し易くなったり、或はこの無端ベルト２５の寿命が短くなったりする原因となる。   The reason why the pulley device with a built-in one-way clutch as described above is used is as follows. The crankshaft of the traveling engine has a fluctuation in rotational speed synchronized with the explosion. If the traveling engine is a diesel engine or a direct injection gasoline engine, the crankshaft The fluctuation of the rotational angular velocity is particularly large. As a result, the traveling speed of the endless belt 25 that spans the drive pulley fixed to the end of the crankshaft also varies finely. On the other hand, the rotating shaft 3 of the alternator 1 that is rotationally driven by the endless belt 25 via the pulley 7a is an inertial mass such as the rotating shaft 3, the rotor 5 fixed to the rotating shaft 3, and the commutator 6 (FIG. 6). Based on this, it does not change so rapidly. Therefore, when the pulley 7a is simply fixed to the rotating shaft 3, the rotational speed of the rotating shaft 3 is decreased as it is when the belt traveling speed is decreased, and the power generation efficiency of the alternator 1 is decreased. At the same time, the endless belt 25 and the pulley 7a tend to rub against each other in accordance with fluctuations in the rotational angular velocity of the crankshaft. As a result, stresses in different directions are repeatedly applied to the endless belt that rubs against the pulley 7a, and slippage is likely to occur between the endless belt 25 and the pulley 7a, or the life of the endless belt 25 is reduced. It may cause shortening.

又、上述の様なオルタネータ１の発電効率の低下、並びにプーリ７ａの外周面と無端ベルト２５の内周面との摩擦に基づく無端ベルト２５の寿命低下は、走行時に加減速を繰り返す事によっても生じる。即ち、加速時には無端ベルト２５側からプーリ７ａ側に駆動力が伝達されるのに対し、減速時には上述の様に慣性に基づいて回転し続けようとするプーリ７ａに、上記無端ベルト２５から制動力が作用する。この制動力に基づいて発電効率が低下するだけでなく、この制動力と上記駆動力とは、上記無端ベルト２５の内周面に対し逆方向の摩擦力として作用するので、やはりこの無端ベルト２５の寿命低下の原因となる。特に、トラックの様に排気ブレーキを備えた車両の場合には、アクセルオフ時に於けるクランクシャフトの回転低下の減速度が著しく、上記制動力に基づいて上記無端ベルト２５の内周面に加わる摩擦力が大きくなる結果、上記発電効率並びに寿命の低下が著しい。   Further, the decrease in the power generation efficiency of the alternator 1 as described above and the decrease in the service life of the endless belt 25 based on the friction between the outer peripheral surface of the pulley 7a and the inner peripheral surface of the endless belt 25 can also be caused by repeated acceleration / deceleration during traveling. Arise. That is, while the driving force is transmitted from the endless belt 25 side to the pulley 7a side during acceleration, the braking force is applied from the endless belt 25 to the pulley 7a that continues to rotate based on inertia as described above during deceleration. Act. Not only the power generation efficiency is reduced based on the braking force, but also the braking force and the driving force act as a frictional force in the opposite direction against the inner peripheral surface of the endless belt 25. Cause a decrease in the service life. In particular, in the case of a vehicle equipped with an exhaust brake such as a truck, the deceleration of the rotation reduction of the crankshaft when the accelerator is off is significant, and the friction applied to the inner peripheral surface of the endless belt 25 based on the braking force As a result of the increased force, the power generation efficiency and lifetime are significantly reduced.

そこで、上述の様なプーリ７ａとして、前記一方向クラッチ内蔵型プーリ装置を使用する。これにより、上記無端ベルト２５の走行速度が一定若しくは上昇傾向にある場合には、一方向クラッチ１１を構成する各ローラ１６が、一方向クラッチ用内輪１５の外周面と一方向クラッチ用外輪１２の内周面との間に形成される円筒状隙間の寸法のうち、直径方向に関する幅が狭くなった部分に食い込んで（ロック状態となって）、上記プーリ７ａから回転軸３への回転力の伝達を自在とする。反対に上記無端ベルト２５の走行速度が低下傾向にある場合には、上記各ローラ１６が上記円筒状隙間のうちの幅が広くなった部分に移動し、これら各ローラ１６が当該部分で転動自在となって（オーバラン状態となって）、上記プーリ７ａと回転軸３との相対回転を自在とする。即ち、上記無端ベルト２５の走行速度が低下傾向にある場合には、上記プーリ７ａの回転角速度を上記回転軸３の回転角速度よりも遅くして、上記無端ベルト２５とプーリ７ａとの当接部が強く擦れ合う事を防止する。この様にして、オルタネータの発電効率を確保すると共に、プーリ７ａと無端ベルト２５との擦れ合い部に作用する応力の方向を一定にし、この無端ベルト２５とプーリ７ａとの間に滑りが発生したり、或はこの無端ベルト２５の寿命が低下する事を防止する。   Therefore, the pulley device with a built-in one-way clutch is used as the pulley 7a as described above. As a result, when the traveling speed of the endless belt 25 is constant or tends to increase, each roller 16 constituting the one-way clutch 11 moves between the outer peripheral surface of the one-way clutch inner ring 15 and the one-way clutch outer ring 12. Of the dimension of the cylindrical gap formed between the inner peripheral surface and the width of the cylindrical gap, the portion that has become narrower in the diametrical direction (in a locked state), the rotational force from the pulley 7a to the rotary shaft 3 is reduced. Freely communicate. On the other hand, when the traveling speed of the endless belt 25 tends to decrease, the rollers 16 move to the widened portion of the cylindrical gap, and the rollers 16 roll on the portions. The pulley 7a and the rotary shaft 3 can be freely rotated relative to each other (in an overrun state). That is, when the traveling speed of the endless belt 25 tends to decrease, the rotational angular speed of the pulley 7a is made slower than the rotational angular speed of the rotating shaft 3, and the contact portion between the endless belt 25 and the pulley 7a Prevents rubbing strongly. In this manner, the power generation efficiency of the alternator is ensured, the direction of the stress acting on the frictional portion between the pulley 7a and the endless belt 25 is made constant, and slip occurs between the endless belt 25 and the pulley 7a. Or the life of the endless belt 25 is prevented from deteriorating.

又、図７に示した一方向クラッチ用内蔵型プーリ装置の場合には、スリーブ９の回転軸３と反対側の端部の外周面に環状板２４を、この端部側に設けたサポート軸受１０と対向させる状態で固定している為、上記スリーブ９の外周面とプーリ７ａの外周面との間の内部空間の軸方向両端部のうち、特に、泥水等の異物が進入し易い、上記回転軸３と反対側の端部での密封性を高められる。   Further, in the case of the one-way clutch built-in pulley device shown in FIG. 7, an annular plate 24 is provided on the outer peripheral surface of the end portion of the sleeve 9 opposite to the rotating shaft 3, and the support bearing is provided on this end portion side. 10 is fixed in a state of being opposed to the outer peripheral surface of the sleeve 9 and the outer peripheral surface of the pulley 7a. The sealing performance at the end opposite to the rotating shaft 3 can be improved.

又、前記特許文献４には、図８に示す様な一方向クラッチ用内蔵型プーリ装置が記載されている。この一方向クラッチ用内蔵型プーリ装置の場合、スリーブ９ａの外周面に外嵌固定した内輪２６の中間部外周面に、カム面１４を形成している。これに対して、プーリ７ａの内周面に内嵌固定した外輪２７の内周面は、軸方向全長に亙り単なる円筒面としている。又、上記外輪２７の軸方向両端寄り部分内周面と、上記内輪２６の軸方向両端寄り部分外周面との間に、それぞれ軸受用保持器２８により転動自在に保持した複数のころ２９、２９を配置している。そして、これら複数のころ２９、２９及び軸受用保持器２８と上記内、外両輪２６、２７の軸方向両端寄り部分とにより、それぞれがラジアルころ軸受である、１対のサポート軸受１０ａ、１０ａを構成している。   Further, Patent Document 4 describes a built-in pulley device for a one-way clutch as shown in FIG. In the case of this one-way clutch built-in pulley device, the cam surface 14 is formed on the outer peripheral surface of the intermediate portion of the inner ring 26 that is fitted and fixed to the outer peripheral surface of the sleeve 9a. On the other hand, the inner peripheral surface of the outer ring 27 fitted and fixed to the inner peripheral surface of the pulley 7a is a simple cylindrical surface over the entire axial length. Also, a plurality of rollers 29 held by a bearing cage 28 between the inner peripheral surface of the outer ring 27 near the both ends in the axial direction and the outer peripheral surface of the inner ring 26 near the both ends in the axial direction, respectively. 29 is arranged. A pair of support bearings 10a and 10a, each of which is a radial roller bearing, are composed of the plurality of rollers 29 and 29 and the bearing retainer 28 and the axially opposite ends of the inner and outer wheels 26 and 27. It is composed.

又、上記外輪２７の軸方向一端部（図８の左端部）に形成した内向フランジ状の鍔部３０と、上記内輪２６の軸方向一端部に形成した外向フランジ状の鍔部３１と、上記プーリ７ａの軸方向一端寄り部分内周面に固定した環状部材３２とにより、このプーリ７ａと上記スリーブ９ａとの軸方向のずれ止めを図ると共に、当該部分にラビリンスシールを構成している。そして、上記プーリ７ａの軸方向一端部に有底円筒状のカバー３３を外嵌固定して、上記プーリ７ａの内周面とスリーブ９ａの外周面との間の内部空間を密封している。   Also, an inward flange-shaped flange 30 formed at one axial end of the outer ring 27 (left end in FIG. 8), an outward flange-shaped flange 31 formed at one axial end of the inner ring 26, and the above The annular member 32 fixed to the inner peripheral surface of the pulley 7a near one end in the axial direction serves to prevent the pulley 7a and the sleeve 9a from slipping in the axial direction, and constitutes a labyrinth seal at that portion. A bottomed cylindrical cover 33 is fitted and fixed to one end of the pulley 7a in the axial direction to seal the internal space between the inner peripheral surface of the pulley 7a and the outer peripheral surface of the sleeve 9a.

上述した従来構造の場合には、それぞれ次の様な不都合が発生する可能性がある。先ず、前述の図７に示した特許文献６に記載された従来構造の第１例の場合には、スリーブ９の外周面とプーリ７ａの内周面との間の内部空間を密封すべく、スリーブ９の回転軸３と反対側の端部の外周面に環状部材２４を外嵌固定している。そして、この環状部材２４が上記スリーブ９に対し、このスリーブ９の中心軸に対し傾斜した状態で固定された場合には、上記環状部材２４によるシール性が悪化するだけでなく、著しい場合には、上記環状部材２４の外径寄り部分が上記一方のサポート軸受１０の外輪１８等と摺接して、回転抵抗が増大する可能性がある。この為、図７に示した従来構造の第１例を実施する場合には、上記環状部材２４の厚さを大きくして、この環状部材２４が傾斜するのを防止する必要がある。但し、この様にした場合には、上記スリーブ９の軸方向長さが大きくなるだけでなく、上記環状部材２４の厚さも、本来の機能上必要とする以上に大きくなる。この為、一方向クラッチ用内蔵型プーリ装置の大型化や重量の増大を招く原因となる。 In the case of the conventional structure described above, the following inconveniences may occur. First, in the case of the first example of the conventional structure described in Patent Document 6 shown in FIG. 7, the inner space between the outer peripheral surface of the sleeve 9 and the inner peripheral surface of the pulley 7a is sealed. An annular member 24 is fitted and fixed to the outer peripheral surface of the end portion of the sleeve 9 opposite to the rotating shaft 3. When the annular member 24 is fixed to the sleeve 9 in an inclined state with respect to the central axis of the sleeve 9, not only the sealing performance by the annular member 24 is deteriorated, but also in a significant case. Further, there is a possibility that a portion near the outer diameter of the annular member 24 is in sliding contact with the outer ring 18 of the one support bearing 10 and the rotation resistance is increased. Therefore, when the first example of the conventional structure shown in FIG. 7 is implemented, it is necessary to increase the thickness of the annular member 24 to prevent the annular member 24 from being inclined. However, in this case, not only the axial length of the sleeve 9 increases, but also the thickness of the annular member 24 becomes larger than necessary for its original function. For this reason, it becomes a cause which causes the enlargement and weight increase of the built-in type pulley device for one-way clutches.

又、前述の図８に示した前記特許文献４に記載された従来構造の第２例の場合には、スリーブ９ａの中間部内周面に形成した雌ねじ部３４に、回転軸３の先端部外周面に形成した雄ねじ部３５を螺合し、更に緊締する事により、上記スリーブ９ａを上記回転軸３の先端部に結合固定できる様にしている。又、この様な結合固定作業は、上記スリーブ９ａの軸方向一端部内周面に形成した雌スプライン状の係合部３６に、図示しない治具の先端部外周面に形成した雄スプライン部状の係合部を係合させつつ行なう。この理由は、上記結合固定作業時に、上記スリーブ９ａが上記回転軸３と共に回転するのを防止する為である。但し、この様な作業は、プーリ７ａの軸方向一端部からカバー３３を取り外した状態で行なう必要がある。従って、図８に示した構造を有する一方向クラッチ内蔵型プーリ装置をオルタネータメーカへ納入する場合には、上記プーリ７ａとカバー３３とを分離した状態で行なう。そして、納入後に、上記オルタネータメーカーに於いて、上記スリーブ９ａと回転軸３とを結合した後、上記プーリ７ａの軸方向一端部に上記カバー３３を取り付ける。この様にしてオルタネータに一方向クラッチ内蔵型プーリ装置を組み付けるのは、この一方向クラッチ内蔵型プーリ装置の搬送作業が面倒になるだけでなく、上記オルタネータメーカーに於いて、作業者の負担が大きくなる為、好ましくない。   Further, in the case of the second example of the conventional structure described in Patent Document 4 shown in FIG. 8 described above, the outer periphery of the distal end portion of the rotary shaft 3 is connected to the female thread portion 34 formed on the inner peripheral surface of the intermediate portion of the sleeve 9a. The sleeve 9a can be coupled and fixed to the distal end portion of the rotary shaft 3 by screwing and tightening the male thread portion 35 formed on the surface. In addition, such a connecting and fixing operation is performed on the female spline-like engagement portion 36 formed on the inner peripheral surface of one end in the axial direction of the sleeve 9a on the male spline-like shape formed on the outer peripheral surface of the tip portion of the jig (not shown). This is performed while engaging the engaging portion. The reason for this is to prevent the sleeve 9a from rotating together with the rotary shaft 3 during the coupling and fixing operation. However, such an operation needs to be performed with the cover 33 removed from one axial end of the pulley 7a. Therefore, when the pulley device with a built-in one-way clutch having the structure shown in FIG. 8 is delivered to the alternator maker, the pulley 7a and the cover 33 are separated from each other. After delivery, the alternator maker connects the sleeve 9a and the rotary shaft 3 and then attaches the cover 33 to one end of the pulley 7a in the axial direction. The assembly of the one-way clutch built-in type pulley device to the alternator in this way not only makes the carrying operation of the one-way clutch built-in type pulley device cumbersome, but also places a heavy burden on the operator in the alternator manufacturer. Therefore, it is not preferable.

特開平７−１３９５５０号公報JP-A-7-139550 特開昭５６−１０１３５３号公報JP-A-56-101353 特開平７−３１７８０７号公報JP 7-317807 A 特開平８−２２６４６２号公報JP-A-8-226462 特開平９−２２９０９７号公報Japanese Patent Laid-Open No. 9-229097 特開平１１−１５９５９９号公報JP 11-159599 A 特公平７−７２５８５号公報Japanese Patent Publication No.7-72585 仏国特許出願公開第２７２６０５９号明細書French Patent Application Publication No. 2726059

本発明は、上述の様な不都合を何れも解消すべく発明したものである。   The present invention has been invented to eliminate all of the above-mentioned disadvantages.

本発明の一方向クラッチ内蔵型プーリ装置は、前述の図７に示した従来構造の第１例と同様に、回転軸の先端部に結合固定自在なスリーブと、このスリーブの周囲にこのスリーブと同心に配置したプーリと、これらスリーブの外周面の軸方向中間部とプーリの内周面の軸方向中間部との間に設け、このプーリが上記スリーブに対し所定方向に相対回転する傾向となる場合にのみ、これらプーリとスリーブとの間での回転力の伝達を自在とする一方向クラッチと、この一方向クラッチを軸方向両側から挟む状態で、上記スリーブの外周面とプーリの内周面との間に設け、このプーリに加わるラジアル荷重を支承しつつこれらスリーブとプーリとの相対回転を自在とした１対のサポート軸受とを備える。 As in the first example of the conventional structure shown in FIG. 7, the one-way clutch built-in pulley device of the present invention includes a sleeve that can be coupled and fixed to the tip of the rotating shaft, and the sleeve around the sleeve. A pulley arranged concentrically and between the axial intermediate portion of the outer peripheral surface of these sleeves and the axial intermediate portion of the inner peripheral surface of the pulley, this pulley tends to rotate relative to the sleeve in a predetermined direction. Only when the one-way clutch that allows the rotational force to be freely transmitted between the pulley and the sleeve, and the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley with the one-way clutch sandwiched from both axial sides. comprises providing a support bearing a pair of the free relative rotation between the sleeves and the pulley while supporting a radial load applied to the pulley between.

特に、本発明の一方向クラッチ内蔵型プーリ装置に於いては、上記プーリの内周面及びスリーブの外周面の間部分のうち、少なくとも上記回転軸の基端側と反対側の端部でこの端部側に設けたサポート軸受の転動体よりも軸方向外側に設けられた、その径方向一端部が相手面と摺接するシール部材と、上記プーリの内周面又はスリーブの外周面の軸方向両端部のうち、少なくとも上記回転軸の基端側と反対側の端部で上記シール部材よりも軸方向外側に外れた部分に、全周に亙り径方向に凹んだ状態で形成した段部と、その径方向一端部を上記段部に嵌合させると共に、その径方向他端部を上記スリーブの外周面又はプーリの内周面に摺接若しくは近接対向させた第二のシール部材とを備える。
又、請求項２に記載した一方向クラッチ内蔵型プーリ装置は、上記シール部材の径方向外端部を、上記プーリとスリーブとのうち、プーリ側の部材に固定しており、上記段部が、上記スリーブの外周面の軸方向両端部のうち、少なくとも上記回転軸の基端側と反対側の端部で上記シール部材よりも軸方向外側に外れた部分に、全周に亙り径方向内側に凹んだ状態で形成したものであり、上記第二のシール部材の径方向内端部を上記段部に嵌合させると共に、この第二のシール部材の径方向外端部を上記プーリの内周面に摺接若しくは近接対向させている。
又、請求項３に記載した一方向クラッチ内蔵型プーリ装置は、上述の本発明の一方向クラッチ内蔵型プーリ装置に於いて、上記段部が係止溝であり、上記第二のシール部材が、芯金と弾性材とで構成され、この弾性材の一部を弾性的に圧縮した状態で上記係止溝に固定したものである。 In particular, in the pulley device with a built-in one-way clutch of the present invention, at least at the end portion on the opposite side of the base end side of the rotary shaft, the portion between the inner peripheral surface of the pulley and the outer peripheral surface of the sleeve. A seal member provided on the outer side in the axial direction from the rolling element of the support bearing provided on the end side, the radial end of which is in sliding contact with the mating surface, and the axial direction of the inner peripheral surface of the pulley or the outer peripheral surface of the sleeve Of the both end portions, at least at the end portion on the opposite side to the base end side of the rotating shaft, a step portion formed in a state of being recessed in the radial direction over the entire circumference at a portion outside the seal member in the axial direction; A second seal member having one end in the radial direction fitted into the stepped portion and the other end in the radial direction being in sliding contact with or in close proximity to the outer peripheral surface of the sleeve or the inner peripheral surface of the pulley. .
Further, in the pulley device with a built-in one-way clutch according to claim 2, the radially outer end portion of the seal member is fixed to a pulley-side member of the pulley and the sleeve, and the step portion is Of the outer circumferential surface of the sleeve, at least the end opposite to the base end side of the rotating shaft and the portion outside the axial direction outside the seal member, the inner circumference in the radial direction. The radially inner end portion of the second seal member is fitted into the stepped portion, and the radially outer end portion of the second seal member is fitted to the inside of the pulley. It is in sliding contact with or in close proximity to the peripheral surface.
The pulley device with a built-in one-way clutch according to claim 3 is the pulley device with a built-in one-way clutch according to the present invention described above, wherein the stepped portion is a locking groove, and the second seal member is It is composed of a cored bar and an elastic material, and a part of this elastic material is elastically compressed and fixed to the locking groove.

上述の様に構成する本発明の一方向クラッチ内蔵型プーリ装置の場合、スリーブの端部外周面とプーリの端部内周面との間に第二のシール部材を設けている為、プーリの内周面及びスリーブの外周面の間部分のうち、少なくとも回転軸の基端側と反対側の端部にシール部材を設けた事と相俟って、これら各サポート軸受及び一方向クラッチの内部空間の密封性を十分に確保できる。更に、上記第二のシール部材の径方向一端部を嵌合固定すべく、上記プーリの内周面又はスリーブの外周面の一部に段部を形成している為、このスリーブ又はプーリの軽量化を図れる。
この為、本発明の一方向クラッチ内蔵型プーリ装置によれば、軽量化を図れる。更に、サポート軸受及び一方向クラッチの内部空間の密封性を十分に確保できる。 In the case of the pulley device with a built-in one-way clutch according to the present invention configured as described above, the second seal member is provided between the outer peripheral surface of the sleeve end and the inner peripheral surface of the pulley end . The inner space of each of the support bearings and the one-way clutch is coupled with the provision of the seal member at least at the end opposite to the base end side of the rotating shaft, between the peripheral surface and the outer peripheral surface of the sleeve. Can be sufficiently secured. Further, a step portion is formed on a part of the inner peripheral surface of the pulley or the outer peripheral surface of the sleeve in order to fit and fix one radial end portion of the second seal member. Can be realized.
For this reason, according to the pulley apparatus with a built-in one-way clutch of the present invention, the weight can be reduced. Furthermore, the sealing performance of the internal space of the support bearing and the one-way clutch can be sufficiently secured.

図１〜３は、本発明の実施例１を示している。本実施例の一方向クラッチ内蔵型プーリ装置は、オルタネータの回転軸３（図６〜８参照）の端部に外嵌固定自在なスリーブ９ｂを有する。又、このスリーブ９ｂの周囲にプーリ７ａを、このスリーブ９ｂと同心に配置している。   1-3 show Example 1 of the present invention. The pulley device with a built-in one-way clutch of the present embodiment has a sleeve 9b that can be fitted and fixed to the end of the rotating shaft 3 (see FIGS. 6 to 8) of the alternator. A pulley 7a is disposed around the sleeve 9b concentrically with the sleeve 9b.

上記スリーブ９ｂは、全体を円筒状に形成しており、上記回転軸３の先端部に外嵌固定して、この回転軸３と共に回転自在である。この為に図示の例では、上記スリーブ９ｂの中間部内周面に雌ねじ部３４を形成し、この雌ねじ部３４と上記回転軸３の端部外周面に形成した雄ねじ部３５（図８参照）とを螺合自在としている。尚、上記回転軸３とスリーブ９ｂとの相対回転を防止する為の構造は、ねじに代えて、スプライン、或は非円筒面同士の嵌合、キー係合等としても良い。又、上記雌ねじ部３４と雄ねじ部３５との螺合作業を容易にする為に、上記スリーブ９ｂの一端部（図１の左端部）内周面に六角孔部３７を形成し、この六角孔部３７に六角レンチ等の工具の先端部を係止自在としている。   The sleeve 9b is formed in a cylindrical shape as a whole, and is fitted and fixed to the distal end portion of the rotating shaft 3 so as to be rotatable together with the rotating shaft 3. For this purpose, in the illustrated example, a female threaded portion 34 is formed on the inner peripheral surface of the intermediate portion of the sleeve 9b, and the female threaded portion 34 and a male threaded portion 35 (see FIG. 8) formed on the outer peripheral surface of the end portion of the rotary shaft 3. Can be screwed together. The structure for preventing the relative rotation between the rotary shaft 3 and the sleeve 9b may be a spline or fitting between non-cylindrical surfaces, key engagement or the like instead of the screw. Further, in order to facilitate the screwing operation of the female screw portion 34 and the male screw portion 35, a hexagonal hole portion 37 is formed on the inner peripheral surface of one end portion (left end portion in FIG. 1) of the sleeve 9b. The tip portion of a tool such as a hexagon wrench can be locked to the portion 37.

上述したスリーブ９ｂの周囲に設けるプーリ７ａは、その内側に次述する１対のサポート軸受１０ｂ、１０ｂ及び一方向クラッチ１１ｂを装着する。又、上記プーリ７ａの片半部（図１の左半部）外周面は、幅方向の断面形状を波形として、ポリＶベルトと呼ばれる無端ベルトの一部を掛け渡し自在としている。   A pulley 7a provided around the sleeve 9b described above is mounted with a pair of support bearings 10b and 10b and a one-way clutch 11b described below on the inside thereof. In addition, the outer peripheral surface of one half of the pulley 7a (the left half in FIG. 1) allows a part of an endless belt called a poly V belt to be freely crossed with a cross-sectional shape in the width direction as a waveform.

又、本実施例の場合には、上記スリーブ９ｂの外周面と上記プーリ７ａの内周面との間に、それぞれが深溝型の玉軸受である、１対のサポート軸受１０ｂ、１０ｂと、ローラクラッチである、１個の一方向クラッチ１１ｂとを設けている。このうちの各サポート軸受１０ｂ、１０ｂは、それぞれ外周面に深溝型の内輪軌道２１を有する内輪１９と、内周面に深溝型の外輪軌道２０を有する外輪１８と、上記内輪軌道２１と外輪軌道２０との間にそれぞれ複数個ずつ転動自在に設けた転動体（玉）２２とから成る。そして、上記外輪１８を上記プーリ７ａの両端寄り部分の内周面に、上記内輪１９を上記スリーブ９ｂの両端寄り部分外周面にそれぞれ全周に亙り形成したスリーブ小径部３９、３９に、それぞれ締り嵌めにより嵌合固定している。又、この状態で上記各内輪１９は、軸方向内端縁を、上記スリーブ小径部３９、３９と上記スリーブ９ｂの本体部分外周面との間の段差面４０、４０に突き当てている。 In the case of the present embodiment, a pair of support bearings 10b and 10b, each of which is a deep groove type ball bearing, between the outer peripheral surface of the sleeve 9b and the inner peripheral surface of the pulley 7a, and a roller A one-way clutch 11b, which is a clutch, is provided. Each of the support bearings 10b and 10b includes an inner ring 19 having a deep groove type inner ring raceway 21 on the outer peripheral surface, an outer ring 18 having a deep groove type outer ring raceway 20 on the inner peripheral surface, and the inner ring raceway 21 and the outer ring raceway. A plurality of rolling elements (balls) 22 that are provided so as to be freely rollable between the two. The outer ring 18 is fastened to the inner peripheral surface of the pulley 7a near the both ends, and the inner ring 19 is fastened to the sleeve small-diameter portions 39, 39 formed on the outer peripheral surface of the sleeve 9b. The fitting is fixed by fitting. Further, in this state, each inner ring 19 abuts the inner edge in the axial direction against the step surfaces 40 and 40 between the sleeve small diameter portions 39 and 39 and the outer peripheral surface of the main body portion of the sleeve 9b.

又、上記各転動体２２は、全体を円環状に形成した軸受用保持器２８により転動自在に保持している。又、上記各内輪１９の両端部外周面と上記各外輪１８の両端部内周面との間には、それぞれシールリング２３、２３を設けている。これら各シールリング２３、２３は、鋼板等の金属板を円環状に形成した芯金と、ゴムの如きエラストマー等の弾性材とにより構成している。そして、これら各シールリング２３、２３の外周縁部を上記各外輪１８の両端部内周面に固定すると共に、上記弾性材の内周縁部を上記各内輪１９の両端部外周面に摺接させている。そして、これら各シールリング２３、２３により、外部から上記複数個の転動体２２が存在する空間内への異物の進入防止を図ると共に、上記各サポート軸受１０ｂ、１０ｂ内に存在するグリースが外部に漏洩するのを防止している。   Each of the rolling elements 22 is held so as to be freely rollable by a bearing retainer 28 formed in an annular shape as a whole. Further, seal rings 23 and 23 are provided between the outer peripheral surfaces at both ends of each inner ring 19 and the inner peripheral surfaces at both ends of each outer ring 18. Each of the seal rings 23 and 23 is constituted by a cored bar in which a metal plate such as a steel plate is formed in an annular shape, and an elastic material such as an elastomer such as rubber. Then, the outer peripheral edge portions of the seal rings 23, 23 are fixed to the inner peripheral surfaces of both end portions of the outer rings 18, and the inner peripheral edge portions of the elastic material are slidably contacted with the outer peripheral surfaces of both end portions of the inner rings 19. Yes. The seal rings 23 and 23 prevent foreign matter from entering the space where the plurality of rolling elements 22 are present from the outside, and the grease present in the support bearings 10b and 10b is exposed to the outside. Prevents leakage.

又、前記一方向クラッチ１１ｂを構成する為、上記スリーブ９ｂの軸方向中間部外周面に一方向クラッチ用内輪１５を、締まり嵌めにより外嵌固定している。この一方向クラッチ用内輪１５は、軸受鋼等の硬質金属製の板材又はＳＣＭ４１５等の浸炭鋼の板材により全体を円筒状に形成し、外周面はカム面１４としている。   Further, in order to constitute the one-way clutch 11b, the one-way clutch inner ring 15 is externally fixed by an interference fit on the outer peripheral surface of the sleeve 9b in the axial direction. The one-way clutch inner ring 15 is formed in a cylindrical shape as a whole by a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415, and the outer peripheral surface is a cam surface 14.

一方、上記プーリ７ａの中間部内周面には一方向クラッチ用外輪４１を、締まり嵌めにより内嵌固定している。やはり軸受鋼等の硬質金属製の板材又はＳＣＭ４１５等の浸炭鋼の板材にプレス加工を施す等により、全体を円筒状に形成した一方向クラッチ用外輪４１は、軸方向両端部に、それぞれ内向フランジ状の鍔部４２ａ、４２ｂを形成している。尚、これら両鍔部４２ａ、４２ｂのうち、一方（図１の左方）の鍔部４２ａは、他の構成各部材と組み合わせる以前に形成する為、上記一方向クラッチ用外輪４１の本体部分と同等の厚さ寸法を有する。これに対して、他方（図１の右方）の鍔部４２ｂは、他の構成各部材と組み合わせた後に形成する為、薄肉にしている。この様な各鍔部４２ａ、４２ｂの軸方向外側面は、前記各サポート軸受１０ｂ、１０ｂを構成する外輪１８、１８の内端面に、それぞれ当接若しくは微小隙間を介して近接対向させている。   On the other hand, an outer ring 41 for a one-way clutch is fitted and fixed to the inner peripheral surface of the intermediate portion of the pulley 7a by an interference fit. The outer ring 41 for a one-way clutch formed into a cylindrical shape by pressing a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415 is also provided with inward flanges at both ends in the axial direction. The shaped collar portions 42a and 42b are formed. Of these two flange portions 42a and 42b, one flange portion 42a (the left side in FIG. 1) is formed before being combined with other constituent members, so that the one-way clutch outer ring 41 has a main body portion. Have equivalent thickness dimensions. On the other hand, the other flange part 42b (on the right side in FIG. 1) is made thin because it is formed after being combined with other constituent members. The outer side surfaces in the axial direction of the flanges 42a and 42b are close to and opposed to the inner end surfaces of the outer rings 18 and 18 constituting the support bearings 10b and 10b, respectively, through contact or minute gaps.

又、前記一方向クラッチ用内輪１５の外周面の複数個所に、ランプ部と呼ばれ、深さが円周方向に関して所定方向に向かう程大きくなる凹部１３を、それぞれこの一方向クラッチ用内輪１５の軸方向に亙り、円周方向に亙り互いに等間隔で形成して、この一方向クラッチ用内輪１５の外周面を前記カム面１４としている。この一方向クラッチ用内輪１５の外周面と上記一方向クラッチ用外輪４１の内周面との間には、円筒状隙間４３が形成されるが、この円筒状隙間４３の寸法のうち、上記一方向クラッチ用外輪４１及び一方向クラッチ用内輪１５の直径方向に関する幅寸法は、上記各凹部１３の最深部に対応する部分ではこの円筒状隙間４３内に設ける複数個のローラ１６の外径よりも大きく、これら各凹部１３から外れた部分ではこれら各ローラ１６の外径よりも小さい。   Further, at a plurality of locations on the outer peripheral surface of the inner ring for one-way clutch 15, concave portions 13, which are called ramp portions, become larger as the depth goes in a predetermined direction with respect to the circumferential direction, respectively. The cam surface 14 is an outer peripheral surface of the inner ring 15 for a one-way clutch that is formed in the axial direction and at equal intervals in the circumferential direction. A cylindrical gap 43 is formed between the outer peripheral surface of the one-way clutch inner ring 15 and the inner peripheral surface of the one-way clutch outer ring 41. The width dimension in the diametrical direction of the outer ring for directional clutch 41 and the inner ring for unidirectional clutch 15 is larger than the outer diameter of the plurality of rollers 16 provided in the cylindrical gap 43 at the portion corresponding to the deepest portion of each recess 13. It is large and is smaller than the outer diameter of each of the rollers 16 at a portion that is separated from each of the recesses 13.

又、上記一方向クラッチ１１ｂは、上記一方向クラッチ用外輪４１の内周面と一方向クラッチ用内輪１５の外周面との間に、合成樹脂により籠型円筒状に形成したクラッチ用保持器１７ａと、それぞれが複数ずつの上記ローラ１６及びばね（図示せず）とを設けて成る。このうちのクラッチ用保持器１７ａは、それぞれが円環状である１対のリム部４４、４４と、これら両リム部４４、４４同士を連結する複数の柱部５９、５９（図３）とから成る。そして、上記各リム部４４、４４の内側面と各柱部５９、５９の側面とにより四周を囲まれた部分を、上記各ローラ１６を転動並びに円周方向に亙る若干の変位自在に保持する為の、複数のポケット４５としている。そして、上記各リム部４４、４４の内周面の内半部複数個所に形成した凸部４６、４６を、上記一方向クラッチ用内輪１５の外周面に形成した凹部１３、１３に係合させる事により、上記クラッチ用保持１７ａを上記一方向クラッチ用内輪１５に、この一方向クラッチ用内輪１５に対する相対回転を不能に装着している。又、上記各ばねは、上述の様なクラッチ用保持１７ａを構成する柱部５９と、上記各ローラ１６との間に設け、これら各ローラ１６を、前記円筒状隙間４３の直径方向に関する幅が狭くなる側に向け、弾性的に押圧している。   The one-way clutch 11b includes a clutch retainer 17a formed in a vertical cylindrical shape with synthetic resin between the inner peripheral surface of the one-way clutch outer ring 41 and the outer peripheral surface of the one-way clutch inner ring 15. And a plurality of the rollers 16 and springs (not shown). Of these, the clutch retainer 17a includes a pair of rim portions 44, 44 each having an annular shape, and a plurality of column portions 59, 59 (FIG. 3) that connect the rim portions 44, 44 to each other. Become. Then, the portions surrounded by the four sides by the inner side surfaces of the rim portions 44 and 44 and the side surfaces of the column portions 59 and 59 are held so that the rollers 16 roll and slightly displace over the circumferential direction. For this purpose, a plurality of pockets 45 are provided. And the convex parts 46 and 46 formed in the inner half part several places of the inner peripheral surface of each said rim | limb parts 44 and 44 are engaged with the recessed parts 13 and 13 formed in the outer peripheral surface of the said inner ring | wheel 15 for one-way clutches. As a result, the clutch holding 17a is mounted on the one-way clutch inner ring 15 so as not to rotate relative to the one-way clutch inner ring 15. Each of the springs is provided between the column portion 59 constituting the clutch holding 17a as described above and each of the rollers 16, and each of the rollers 16 has a width in the diameter direction of the cylindrical gap 43. It is elastically pressed toward the narrower side.

又、本実施例の場合には、上記クラッチ用保持器１７ａを構成する１対のリム部４４、４４のうち、一方（図１の右方）のリム部４４の軸方向外半部内周面に抑え片４７を、他方（図１の左方）のリム部４４の軸方向外半部内周面に抑え鍔部４８を、それぞれ形成している。上記抑え片４７は、上記一方のリム部４４の軸方向外半部内周面の円周方向に関して１乃至複数個所に設けており、図３に詳示するように構成している。即ち、上記一方のリム部４４の軸方向外半部内周面で、円周方向に隣り合う凸部４６、４６同士の間部分に逃げ溝５０を、上記一方のリム部４４の内周面と外端面とに開口する状態で形成している。そして、上記逃げ溝５０の側面の内径側半部の円周方向中間部に抑え片４７を、軸方向に突出する状態で形成している。この抑え片４７の先端部内周面には係合突部４９を、径方向内方に突出する状態で設けている。そして、この係合突部４９と、上記他方のリム部４４の外半部内周面に、全周に亙り、或は円周方向に関して間欠的に形成した抑え鍔部４８とにより、上記一方向クラッチ用内輪１５を軸方向両側から挟持している。   Further, in the case of this embodiment, the axially outer half inner peripheral surface of one rim portion 44 (right side in FIG. 1) of the pair of rim portions 44, 44 constituting the clutch retainer 17a. The restraining piece 47 is formed on the inner peripheral surface of the outer half portion in the axial direction of the rim portion 44 on the other side (left side in FIG. 1). The holding piece 47 is provided at one or a plurality of locations in the circumferential direction of the inner circumferential surface of the outer half portion in the axial direction of the one rim portion 44, and is configured as shown in detail in FIG. That is, on the inner circumferential surface of the outer half portion in the axial direction of the one rim portion 44, the relief groove 50 is formed between the convex portions 46, 46 adjacent in the circumferential direction, and the inner circumferential surface of the one rim portion 44. It forms in the state opened to an outer end surface. And the restraining piece 47 is formed in the state which protrudes to the axial direction in the circumferential direction intermediate part of the internal diameter side half part of the side surface of the said relief groove 50. As shown in FIG. An engaging protrusion 49 is provided on the inner peripheral surface of the tip of the holding piece 47 so as to protrude radially inward. The one-way direction is formed by the engaging protrusion 49 and the holding collar 48 formed on the inner circumferential surface of the outer half of the other rim portion 44 over the entire circumference or intermittently in the circumferential direction. The clutch inner ring 15 is clamped from both axial sides.

前記一方向クラッチ１１ｂを構成する各ローラ１６は、上記一方向クラッチ用内輪１５と一方向クラッチ用外輪４１とが所定方向に相対回転する場合には、これら一方向クラッチ用内輪１５の外周面と一方向クラッチ用外輪４１の内周面との間の円筒状隙間４３のうち、直径方向に関する幅が狭くなった部分に食い込み、これら一方向クラッチ用内輪１５と一方向クラッチ用外輪４１との間で回転力の伝達を行なわせる。これに対して、上記一方向クラッチ用内輪１５と一方向クラッチ用外輪４１とが逆方向に相対回転する場合には、上記各ローラ１６が、上記円筒状隙間４３のうち、直径方向に関する幅が広くなった部分に移動して当該部分で転動自在となり、これら一方向クラッチ用内輪１５と一方向クラッチ用外輪４１との間で回転力の伝達を行なわせない。尚、この様な一方向クラッチ１１ｂの基本的な構成及び作用は、前述の図７〜８に示した従来構造の場合と同様であり、本発明の要旨でもない為、これ以上の詳しい説明は省略する。   When the one-way clutch inner ring 15 and the one-way clutch outer ring 41 rotate relative to each other in a predetermined direction, the rollers 16 constituting the one-way clutch 11b are arranged on the outer peripheral surface of the one-way clutch inner ring 15; Of the cylindrical gap 43 between the outer ring 41 for the one-way clutch and the inner peripheral surface of the one-way clutch 41, the portion that has a narrower width in the diametrical direction bites into the space between the inner ring 15 for the one-way clutch and the outer ring 41 for the one-way clutch. To transmit torque. On the other hand, when the inner ring 15 for one-way clutch and the outer ring 41 for one-way clutch rotate in the opposite directions, each roller 16 has a width in the diameter direction in the cylindrical gap 43. It moves to the widened part and becomes free to roll in that part, and no rotational force is transmitted between the inner ring 15 for one-way clutch and the outer ring 41 for one-way clutch. The basic configuration and operation of such a one-way clutch 11b is the same as that of the conventional structure shown in FIGS. 7 to 8 and is not the gist of the present invention. Omitted.

特に、本実施例の場合には、前記プーリ７ａの前記回転軸３の基端側と反対側の端部である、軸方向一端部の内周面で、この軸方向一端部側に設けたサポート軸受１０ｂを構成する外輪１８を内嵌固定する部分よりも軸方向外側に外れた部分に、請求項に記載した段部に相当する、係止溝５１を形成している。この係止溝５１は、上記各サポート軸受１０ｂを構成する外輪１８及び一方向クラッチ１１ｂを構成する一方向クラッチ用外輪４１を内嵌固定する本体部分内周面よりも外径側に、全周に亙り凹んだ状態で形成している。そして、上記プーリ７ａの軸方向一端部内周面で、上記係止溝５１と軸方向外側に隣り合う部分に鍔部５２を、全周に亙り内径側に突出する状態で形成している。又、この鍔部５２の内径は、上記本体部分の内周面の内径よりも大きくしている。従って、この鍔部５２の内周縁部が、上記本体部分の内周面よりも内径側に突出する事はない。そして、上記係止溝５１の軸方向外端側側面を、上記プーリ７ａの内径側に向かう程軸方向外端側に位置する方向に傾斜したテーパ面としている。これに対して、上記係止溝５１の軸方向中央部側側面は、上記プーリ７ａの中心軸に対し直交する仮想平面上に位置させている。 In particular, in the case of the present embodiment , the pulley 7a is provided on the one end side in the axial direction on the inner peripheral surface of the one end portion in the axial direction, which is the end portion on the opposite side to the base end side of the rotating shaft 3. A locking groove 51 corresponding to the step portion described in the claims is formed in a portion that is dislocated axially outward from a portion in which the outer ring 18 constituting the support bearing 10b is fitted and fixed. The locking groove 51 is arranged on the outer diameter side with respect to the outer peripheral side of the body portion inner peripheral surface on which the outer ring 18 constituting the support bearings 10b and the one-way clutch outer ring 41 constituting the one-way clutch 11b are fitted and fixed. It is formed in a state of being recessed. A flange portion 52 is formed on the inner peripheral surface of one end of the pulley 7a in the axial direction at a portion adjacent to the locking groove 51 in the axial direction so as to protrude to the inner diameter side over the entire circumference. Further, the inner diameter of the flange portion 52 is larger than the inner diameter of the inner peripheral surface of the main body portion. Therefore, the inner peripheral edge portion of the flange portion 52 does not protrude toward the inner diameter side from the inner peripheral surface of the main body portion. And the axial direction outer end side surface of the said locking groove 51 is made into the taper surface which inclined in the direction located in an axial direction outer end side, so that it goes to the internal diameter side of the said pulley 7a. On the other hand, the axially central side surface of the locking groove 51 is positioned on a virtual plane perpendicular to the central axis of the pulley 7a.

そして、上記プーリ７ａの軸方向一端部内周面と前記スリーブ９ｂの軸方向一端部外周面との間に請求項に記載した第二のシール部材に相当する、第二のシールリング５３を、その外周縁部を上記係止溝５１に内嵌固定する状態で設けている。この第二のシールリング５３は、鋼板（例えばＳＰＣＣ）等の金属板を円環状に形成した芯金５４と、ゴム（例えばＮＢＲ）の如きエラストマー等の弾性材５５とにより構成したもので、断面を略Ｌ字形としている。そして、上記係止溝５１に、上記弾性材５５の外周縁部に設けた折れ曲がり部５６の一部を弾性的に圧縮した状態で係止する事により、上記第二のシールリング５３の外周縁部を上記プーリ７ａの軸方向一端部に内嵌固定している。この際、上記折れ曲がり部５６の先端面（図１、２の右端面）を、上記係止溝５１の軸方向中央部側側面に突き当てている。又、上記弾性材５５の内周縁部に設けたシールリップ５７の先端縁（内周縁）を、上記スリーブ９ｂの軸方向一端部外周面に、この外周面との間に所定の締め代を持たせた状態で摺接させている。   A second seal ring 53 corresponding to the second seal member described in the claims is provided between the inner peripheral surface of the one axial end of the pulley 7a and the outer peripheral surface of the one axial end of the sleeve 9b. The outer peripheral edge portion is provided in a state of being fitted and fixed in the locking groove 51. The second seal ring 53 is constituted by a cored bar 54 in which a metal plate such as a steel plate (for example, SPCC) is formed in an annular shape, and an elastic material 55 such as an elastomer such as rubber (for example, NBR). Is substantially L-shaped. Then, the outer peripheral edge of the second seal ring 53 is locked to the locking groove 51 in a state where a part of the bent portion 56 provided on the outer peripheral edge of the elastic material 55 is elastically compressed. This part is fitted and fixed to one end in the axial direction of the pulley 7a. At this time, the front end surface of the bent portion 56 (the right end surface in FIGS. 1 and 2) is abutted against the axially central side surface of the locking groove 51. Further, a predetermined tightening margin is provided between the outer peripheral surface of the end edge (inner peripheral edge) of the seal lip 57 provided on the inner peripheral edge of the elastic material 55 and the outer peripheral surface of one end of the sleeve 9b in the axial direction. It is slid in contact.

更に、本実施例の場合には、上記第二のシールリング５３の外径寄り部分の円周方向に関して１乃至複数個所に通孔５８を、この第二のシールリング５３の両側面を貫通する状態で形成している。この通孔５８は、上記第二のシールリング５３の軸方向外端側に向かう程外径側に位置する方向に傾斜させている。従って、この通孔５８の外部空間側の開口端は、この通孔５８の内部空間側の開口端よりも外径側に位置している。   Further, in the case of the present embodiment, one or a plurality of through holes 58 are passed through the both sides of the second seal ring 53 with respect to the circumferential direction of the portion near the outer diameter of the second seal ring 53. It is formed in a state. The through hole 58 is inclined in a direction positioned on the outer diameter side toward the outer end side in the axial direction of the second seal ring 53. Therefore, the opening end of the through hole 58 on the outer space side is located on the outer diameter side than the opening end of the through hole 58 on the inner space side.

上述の様に構成する本実施例の一方向クラッチ内蔵型プーリ装置の場合、スリーブ９ｂの軸方向一端部外周面とプーリ７ａの軸方向一端部内周面との間に第二のシールリング５３を設けている為、各サポート軸受１０ｂ、１０ｂの軸方向両端部にシールリング２３、２３を設けた事と相俟って、これら各サポート軸受１０ｂ、１０ｂ及び一方向クラッチ１１ｂの内部空間の密封性を十分に確保できる。 In the case of the pulley device with a built-in one-way clutch of the present embodiment configured as described above, the second seal ring 53 is provided between the outer peripheral surface of the sleeve 9b in the axial direction and the inner peripheral surface of the pulley 7a. Therefore, in combination with the provision of the seal rings 23 and 23 at both ends in the axial direction of the support bearings 10b and 10b, the sealability of the internal spaces of the support bearings 10b and 10b and the one-way clutch 11b is provided. Can be secured sufficiently.

更に、上記第二のシールリング５３の外周縁部を内嵌固定すべく、上記プーリ７ａの軸方向一端部内周面に係止溝５１を形成している為、このプーリ７ａの軽量化を図れる。更に、本実施例の場合には、上記係止溝５１の底面の直径及びこの係止溝５１と軸方向外側に隣り合う状態で設けた鍔部５２の内径を、軸方向一端側に設けるサポート軸受１０ｂを構成する外輪１８を内嵌固定する、上記プーリ７ａの本体部分の内径よりも大きくしている。この為、上記サポート軸受１０ｂを上記プーリ７ａ及びスリーブ９ｂに対し圧入する長さを小さくできて、上記サポート軸受１０ｂの圧入作業の容易化を図れる。又、本実施例の場合には、各サポート軸受１０ｂ、１０ｂを一方向クラッチ１１ｂと独立して設けている為、これら各サポート軸受１０ｂ、１０ｂを上記スリーブ９ｂ及びプーリ７ａの軸方向反対側から圧入する事ができて、これら各サポート軸受１０ｂ、１０ｂの圧入作業の容易化を図れる。   Further, since the locking groove 51 is formed on the inner peripheral surface of the one axial end portion of the pulley 7a in order to fit and fix the outer peripheral edge portion of the second seal ring 53, the weight of the pulley 7a can be reduced. . Further, in the case of this embodiment, a support is provided in which the diameter of the bottom surface of the locking groove 51 and the inner diameter of the flange 52 provided in a state adjacent to the locking groove 51 on the outer side in the axial direction are provided on one axial end side. The outer ring 18 constituting the bearing 10b is set to be larger than the inner diameter of the main body portion of the pulley 7a to be fitted and fixed. For this reason, the length of press-fitting the support bearing 10b into the pulley 7a and the sleeve 9b can be reduced, and the press-fitting work of the support bearing 10b can be facilitated. In the present embodiment, since the support bearings 10b and 10b are provided independently of the one-way clutch 11b, the support bearings 10b and 10b are connected to the sleeve 9b and the pulley 7a from the opposite side in the axial direction. It is possible to press-fit, and it is possible to facilitate the press-fitting work of these support bearings 10b and 10b.

又、本実施例の場合には、上記係止溝５１に、上記第二のシールリング５３を構成する弾性材５５の外周縁部に設けた折れ曲がり部５６の一部を弾性的に圧縮した状態で係止する事により、上記第二のシールリング５３の外周縁部を上記係止溝５１に内嵌固定している。この様に大きく弾性変形する弾性材５５から成る折れ曲がり部５６の一部を、上記係止溝５１に弾性的に圧縮した状態で係止する作業は、例えば数１００Ｎ程度の小さい力により、容易に行なえる。又、この様に第二のシールリング５３の外周縁部を上記プーリ７ａの一部に係止した状態では、上記折れ曲がり部５６の外径寄り部分が上記係止溝５１の両側面により弾性的に挟持される為、使用時に、上記第二のシールリング５３が上記プーリ７ａの軸方向一端部から抜け出る事を防止できる。   Further, in the case of the present embodiment, a state in which a part of the bent portion 56 provided on the outer peripheral edge portion of the elastic material 55 constituting the second seal ring 53 is elastically compressed in the locking groove 51. The outer peripheral edge portion of the second seal ring 53 is fitted and fixed in the locking groove 51 by locking with the locking groove 51. The operation of locking a part of the bent portion 56 formed of the elastic material 55 that is elastically deformed in this manner in a state of being elastically compressed in the locking groove 51 is easily performed with a small force of about several hundred N, for example. Yes. Further, in the state where the outer peripheral edge of the second seal ring 53 is locked to a part of the pulley 7 a in this way, the portion closer to the outer diameter of the bent portion 56 is more elastic by both side surfaces of the locking groove 51. Therefore, it is possible to prevent the second seal ring 53 from coming off from one end of the pulley 7a in the axial direction during use.

更に、上記第二のシールリング５３の折れ曲がり部５６の先端面は、上記係止溝５１の中央部側側面に突き当てている為、上記第二のシールリング５３が上記プーリ７ａに対し、このプーリ７ａの中心軸に対し傾斜した状態で固定されにくくなる。この為、上記プーリ７ａの軸方向一端部で、軸方向一端側のサポート軸受１０ｂよりも軸方向外側に突出する部分の軸方向長さを小さくしても、上記第二のシールリング５３の内周縁が前記スリーブ９ｂの外周面から外れるのを防止して、十分なシール性を確保できる。この為、シール性を確保しつつ、一方向クラッチ用内蔵型プーリ装置の小型化・軽量化を図れる。   Furthermore, since the front end surface of the bent portion 56 of the second seal ring 53 abuts against the central side surface of the locking groove 51, the second seal ring 53 is against the pulley 7a. It becomes difficult to be fixed in a state of being inclined with respect to the central axis of the pulley 7a. For this reason, even if the axial length of the portion of the pulley 7a that protrudes outward in the axial direction from the support bearing 10b on the axial end side of the pulley 7a is reduced, It is possible to prevent the peripheral edge from being detached from the outer peripheral surface of the sleeve 9b, and to ensure a sufficient sealing performance. Therefore, it is possible to reduce the size and weight of the built-in pulley device for a one-way clutch while ensuring sealing performance.

更に、本実施例の場合には、上記第二のシールリング５３の外径寄り部分に通孔５８を形成している。この為、万一、上記プーリ７ａの内周面とスリーブ９ｂの外周面との間の内部空間内に泥水等の異物が進入した場合でも、この異物を、上記通孔５８を通じて外部に容易に排出できる。即ち、万一、上記内部空間内に異物が進入した場合でも、使用時にこの異物に遠心力が作用する事により、この異物は外径側に振り飛ばされる。そして、この外径側に振り飛ばされた異物が、上記通孔５８の内部空間側開口端からこの通孔５８内に進入した後、この開口端よりも更に外径側に位置する、外部空間側開口端を通じて外部に排出される。従って、万一、上記内部空間内に異物が進入した場合でも、この異物を外部に容易に排出できて、この異物が前記各サポート軸受１０ｂ、１０ｂ及び一方向クラッチ１１ｂの内部に迄達する事を防止できる。   Further, in the case of the present embodiment, a through hole 58 is formed in a portion near the outer diameter of the second seal ring 53. For this reason, even if foreign matter such as muddy water enters the internal space between the inner peripheral surface of the pulley 7a and the outer peripheral surface of the sleeve 9b, the foreign matter can be easily removed to the outside through the through hole 58. Can be discharged. That is, even if a foreign matter enters the internal space, the foreign matter is shaken off to the outer diameter side by a centrifugal force acting on the foreign matter during use. After the foreign matter shaken off to the outer diameter side enters the through hole 58 from the inner space side opening end of the through hole 58, the outer space is located further on the outer diameter side than the opening end. It is discharged to the outside through the side opening end. Therefore, even if a foreign object enters the internal space, the foreign object can be easily discharged to the outside, and the foreign object reaches the inside of each of the support bearings 10b and 10b and the one-way clutch 11b. Can be prevented.

更に、本実施例の場合には、クラッチ用保持器１７ａの軸方向両端部内周面に設けた抑え片４７の係合突部４９と抑え鍔部４８とにより、一方向クラッチ用内輪１５を軸方向両側から挟持している。この為、前記プーリ７ａとスリーブ９ｂとが相対回転するオーバラン時に、上記クラッチ用保持器１７ａが軸方向に振れ動いて、このクラッチ用保持器１７ａの軸方向両端面と一方向クラッチ用外輪４１の軸方向両端部に設けた鍔部４２ａ、４２ｂの内側面とが摺接する事を防止できる。この結果、この摺接に基づく摩擦熱の発生を防止して、一方向クラッチ１１ｂを潤滑するグリースの熱劣化を防止できると共に、上記クラッチ用保持器１７ａの耐久性を十分に確保できる。   Furthermore, in the case of the present embodiment, the inner ring 15 for one-way clutch is pivoted by the engaging protrusions 49 and the restraining flanges 48 of the restraining pieces 47 provided on the inner peripheral surfaces of both axial ends of the clutch retainer 17a. It is clamped from both directions. Therefore, at the time of overrun in which the pulley 7a and the sleeve 9b rotate relative to each other, the clutch retainer 17a swings in the axial direction, and both axial end surfaces of the clutch retainer 17a and the one-way clutch outer ring 41 It is possible to prevent sliding contact between the inner surfaces of the flange portions 42a and 42b provided at both axial end portions. As a result, the generation of frictional heat due to the sliding contact can be prevented, the thermal deterioration of the grease that lubricates the one-way clutch 11b can be prevented, and the durability of the clutch retainer 17a can be sufficiently ensured.

次に、図４は、本発明の実施例２を示している。本実施例の場合には、プーリ７ａの軸方向一端部内周面に、ＳＰＣＣの如き鋼板等の金属板を曲げ形成して成る第二のシールリング５３ａを内嵌固定している。この第二のシールリング５３ａは、金属板を曲げ形成する事により、断面コ字形で全体を円輪状としたものであり、円輪部６０と、この円輪部６０の外周縁部及び内周縁部から同方向に直角に折れ曲がった、外径側円筒部６１及び内径側円筒部６２とから成る。又、上記プーリ７ａの軸方向一端部（図４の左端部）内周面で、軸方向一端側のサポート軸受１０ｂを構成する外輪１８を内嵌固定する部分よりも軸方向外側に外れた部分に段部６３を、上記プーリ７ａの本体部分内周面よりも外径側に、全周に亙り凹んだ状態で形成している。一方、スリーブ９ｂの軸方向一端部外周面で上記段部６３と対向する部分に第二の段部６４を、軸方向一端側のサポート軸受１０ｂを構成する内輪１９を外嵌固定するスリーブ小径部３９の外周面よりも内径側に、全周に亙り凹んだ状態で形成している。 Next, FIG. 4 shows Embodiment 2 of the present invention. In the case of the present embodiment, a second seal ring 53a formed by bending a metal plate such as a steel plate such as SPCC is fitted and fixed to the inner peripheral surface of one end of the pulley 7a in the axial direction. The second seal ring 53a is formed by bending a metal plate to form an annular shape as a whole with a U-shaped cross section. The annular portion 60 and the outer and inner circumferential edges of the annular portion 60 It comprises an outer diameter side cylindrical portion 61 and an inner diameter side cylindrical portion 62 that are bent at right angles in the same direction from the portion. Further, a portion of the inner peripheral surface of the pulley 7a in the axial direction (left end portion in FIG. 4) that is disengaged outward in the axial direction from the portion in which the outer ring 18 constituting the support bearing 10b on the axial end side is fitted and fixed. The step portion 63 is formed on the outer diameter side of the main body portion inner peripheral surface of the pulley 7a so as to be recessed over the entire circumference. On the other hand, on the outer peripheral surface of one end portion in the axial direction of the sleeve 9b, the second step portion 64 is provided at a portion facing the step portion 63, and the sleeve small diameter portion for externally fixing the inner ring 19 constituting the support bearing 10b on the one end side in the axial direction. It is formed in a state of being recessed over the entire circumference on the inner diameter side of the outer peripheral surface of 39.

そして、上記プーリ７ａの軸方向一端部内周面に形成した段部６３に、上記第二のシールリング５３ａを構成する外径側円筒部６１を締り嵌めにより内嵌固定すると共に、この第二のシールリング５３ａを構成する内径側円筒部６２の内周面を、上記第二の段部６４の外周面に、微小隙間を介して対向させている。又、上記第二のシールリング５３ａを構成する円輪部６０の片側面の外径寄り部分を、上記プーリ７ａの本体部分内周面と上記段部６３との間の段差面６５に突き当てている。更に、本実施例の場合には、上記円輪部６０の外径寄り部分で上記段差面６５よりも内径側に外れた部分に通孔６６を、軸方向に貫通する状態で形成している。   Then, the outer diameter side cylindrical portion 61 constituting the second seal ring 53a is internally fitted and fixed to the step portion 63 formed on the inner peripheral surface of the one axial end portion of the pulley 7a. The inner peripheral surface of the inner diameter side cylindrical portion 62 constituting the seal ring 53a is opposed to the outer peripheral surface of the second stepped portion 64 via a minute gap. Further, the outer diameter portion of one side surface of the annular ring portion 60 constituting the second seal ring 53a is abutted against the step surface 65 between the inner peripheral surface of the main body portion of the pulley 7a and the step portion 63. ing. Further, in the case of the present embodiment, a through hole 66 is formed in a portion penetrating in the axial direction at a portion near the outer diameter of the annular ring portion 60 and deviating from the step surface 65 to the inner diameter side. .

上述の様に構成する本実施例の場合には、第二のシールリング５３ａを構成する内径側円筒部６２の内周面とスリーブ９ｂの軸方向一端部外周面に形成した第二の段部６４の外周面とによりラビリンスシールを構成している。そして、このラビリンスシールにより、各サポート軸受１０ｂ、１０ｂの軸方向両端部にシールリング２３、２３を設けた事と相俟って、これら各サポート軸受１０ｂ、１０ｂ及び一方向クラッチ１１ｂの内部空間の密封性を十分に確保できる。更に、本実施例の場合には、上記第二のシールリング５３ａを構成する円輪部６０の片側面の外径寄り部分を、上記段差面６５に突き当てている為、上記第二のシールリング５３ａが上記プーリ７ａに対し傾斜した状態で固定されにくくなり、シール性を確保しつつ、一方向クラッチ用内蔵型プーリ装置の小型化・軽量化を図れる。   In the case of the present embodiment configured as described above, the second step portion formed on the inner peripheral surface of the inner diameter side cylindrical portion 62 constituting the second seal ring 53a and the outer peripheral surface of one end portion in the axial direction of the sleeve 9b. A labyrinth seal is constituted by 64 outer peripheral surfaces. And by this labyrinth seal, coupled with the fact that the seal rings 23, 23 are provided at both axial ends of the support bearings 10b, 10b, the internal spaces of the support bearings 10b, 10b and the one-way clutch 11b A sufficient sealing property can be secured. Further, in the case of the present embodiment, the portion close to the outer diameter on one side surface of the annular portion 60 constituting the second seal ring 53a is abutted against the step surface 65, so that the second seal The ring 53a is less likely to be fixed in an inclined state with respect to the pulley 7a, and the one-way clutch built-in pulley device can be reduced in size and weight while ensuring sealing performance.

又、本実施例の場合には、万一、プーリ７ａの内周面とスリーブ９ｂの外周面との間の内部空間内に泥水等の異物が進入した場合でも、上記第二のシールリング５３ａの外径寄り部分に形成した通孔６６を通じて、上記異物を外部に容易に排出できる。又、本実施例の場合には、上記スリーブ９ｂの軸方向一端部外周面に第二の段部６４を、軸方向一端側のサポート軸受１０ｂを構成する内輪１９を外嵌固定するスリーブ小径部３９の外周面よりも内径側に、全周に亙り凹んだ状態で形成している。この為、上記第二の段部６４を、上記内輪１９を圧入する際の案内面として用いる事ができて、圧入作業の更なる容易化を図れる。
その他の構成及び作用に就いては、上述の図１〜３に示した実施例１の場合と同様である為、重複する説明は省略する。 In the case of the present embodiment, even if foreign matter such as muddy water enters the internal space between the inner peripheral surface of the pulley 7a and the outer peripheral surface of the sleeve 9b, the second seal ring 53a is used. The foreign matter can be easily discharged to the outside through a through hole 66 formed in a portion near the outer diameter. In the case of the present embodiment, the sleeve 9b has a second stepped portion 64 on the outer peripheral surface of one axial end portion of the sleeve 9b, and a sleeve small diameter portion for externally fixing the inner ring 19 constituting the support bearing 10b on one axial end side. It is formed in a state of being recessed over the entire circumference on the inner diameter side of the outer peripheral surface of 39. Therefore, the second step portion 64 can be used as a guide surface when the inner ring 19 is press-fitted, and the press-fitting operation can be further facilitated.
Other configurations and operations are the same as those in the first embodiment shown in FIGS.

次に、図５は、本発明の実施例３を示している。本実施例の場合には、上述の図４に示した実施例２の場合と異なり、プーリ７ａの軸方向一端部（図５の左端部）内周面に段部６３（図４）を形成せず、このプーリ７ａの内周面を、実質的に（軸方向両端部内周面に形成した面取り部を除いて）単なる円筒面としている。そして、本実施例の場合には、第二のシールリング５３ａの内周縁部に形成した内径側円筒面部６２を、スリーブ９ｂの軸方向一端部外周面に形成した第二の段部６４に外嵌固定している。そして、上記第二のシールリング５３ａを構成する円輪部６０の片側面の内径寄り部分を、上記第二の段部６４と本体部分外周面との間の段差面６７に突き当てている。これと共に、上記第二のシールリング５３ａを構成する外径側円筒部６１の外周面を、上記プーリ７ａの一端部内周面に微小隙間を介して対向させている。本実施例の場合には、上記スリーブ９ｂの軸方向一端部外周面に形成した第二の段部６４が、請求項に記載した段部に相当する。   Next, FIG. 5 shows Embodiment 3 of the present invention. In the present embodiment, unlike the second embodiment shown in FIG. 4 described above, a stepped portion 63 (FIG. 4) is formed on the inner peripheral surface of one end portion (left end portion in FIG. 5) in the axial direction of the pulley 7a. Instead, the inner peripheral surface of the pulley 7a is substantially a simple cylindrical surface (excluding the chamfered portions formed on the inner peripheral surfaces at both axial ends). In the case of the present embodiment, the inner diameter side cylindrical surface portion 62 formed on the inner peripheral edge portion of the second seal ring 53a is externally attached to the second step portion 64 formed on the outer peripheral surface of one end portion in the axial direction of the sleeve 9b. It is fitted and fixed. Then, a portion closer to the inner diameter of one side surface of the annular portion 60 constituting the second seal ring 53a is abutted against a step surface 67 between the second step portion 64 and the outer peripheral surface of the main body portion. At the same time, the outer peripheral surface of the outer diameter side cylindrical portion 61 constituting the second seal ring 53a is opposed to the inner peripheral surface of one end portion of the pulley 7a via a minute gap. In the case of the present embodiment, the second step portion 64 formed on the outer peripheral surface of the axial end portion of the sleeve 9b corresponds to the step portion described in the claims.

上述の様に構成する本実施例の場合には、第二のシールリング５３ａを構成する外径側円筒部６１の外周面とプーリ７ａの軸方向一端部内周面とによりラビリンスシールを構成している。そして、このラビリンスシールにより、各サポート軸受１０ｂ、１０ｂにシールリング２３、２３を設けた事と相俟って、これら各サポート軸受１０ｂ、１０ｂ及び一方向クラッチ１１ｂの内部空間の密封性を十分に確保できる。尚、図示の例の場合には、シールリング２３、２３を、上記各サポート軸受１０ｂ、１０ｂの軸方向外端部にのみ１個ずつ設けて、これら各サポート軸受１０ｂ、１０ｂを所謂片側シール構造としている。これに伴って、これら両サポート軸受１０ｂ、１０ｂ及び一方向クラッチ１１ｂの内部には、共通のグリースを封入する。   In the case of the present embodiment configured as described above, a labyrinth seal is configured by the outer peripheral surface of the outer diameter side cylindrical portion 61 and the inner peripheral surface of one axial end portion of the pulley 7a constituting the second seal ring 53a. Yes. This labyrinth seal, together with the provision of the seal rings 23 and 23 on the support bearings 10b and 10b, sufficiently seals the internal spaces of the support bearings 10b and 10b and the one-way clutch 11b. It can be secured. In the case of the illustrated example, one seal ring 23, 23 is provided only at the outer end in the axial direction of each of the support bearings 10b, 10b, and each of the support bearings 10b, 10b is a so-called one-side seal structure. It is said. Along with this, common grease is sealed inside these support bearings 10b and 10b and the one-way clutch 11b.

更に、本実施例の場合には、上記第二のシールリング５３ａの一部に通孔を形成する事なく、プーリ７ａの内周面とスリーブ９ｂの外周面との間の内部空間内に進入した泥水等の異物を、外部に容易に排出できる。即ち、万一、上記内部空間内に異物が進入した場合には、使用時に、この異物に遠心力が作用して、この異物が外径側に振り飛ばされる。そして、この振り飛ばされた異物が、上記外径側円筒部６１の外周面と上記プーリ７ａの軸方向一端部内周面との間に形成される円環状隙間を通じて、外部に容易に排出される。この為、上記第二のシールリング５３ａに上記通孔を形成する必要がなくなり、この第二のシールリング５３ａのコストを低減できる。
その他の構成及び作用に就いては、前述の図４に示した実施例２の場合と同様である為、重複する説明は省略する。 Further, in the case of the present embodiment, without entering a hole in a part of the second seal ring 53a, it enters the internal space between the inner peripheral surface of the pulley 7a and the outer peripheral surface of the sleeve 9b. Foreign matter such as muddy water can be easily discharged to the outside. That is, in the unlikely event that foreign matter enters the internal space, centrifugal force acts on the foreign matter during use, and the foreign matter is shaken off to the outer diameter side. The scattered foreign matter is easily discharged to the outside through an annular gap formed between the outer peripheral surface of the outer diameter side cylindrical portion 61 and the inner peripheral surface of one end portion in the axial direction of the pulley 7a. . For this reason, it is not necessary to form the through hole in the second seal ring 53a, and the cost of the second seal ring 53a can be reduced.
Since other configurations and operations are the same as those in the second embodiment shown in FIG. 4 described above, a duplicate description is omitted.

尚、上述した各実施例の場合には、各サポート軸受１０ｂ、１０ｂをラジアル玉軸受とした場合に就いて説明したが、本発明はこの様な構造に限定するものではない。各サポート軸受としてころ軸受を用いた場合でも、本発明を適用できる。又、一方向クラッチ１１ｂに就いても、上述した各実施例の場合の様に複数個のロック部材としてローラを使用するローラクラッチを用いた構造に限定するものではなく、複数個のロック部材としてスプラグ等のカムを使用するカム式のものを用いた構造にも、本発明を適用できる。   In addition, in the case of each Example mentioned above, although demonstrated about the case where each support bearing 10b, 10b was a radial ball bearing, this invention is not limited to such a structure. The present invention can be applied even when a roller bearing is used as each support bearing. Also, the one-way clutch 11b is not limited to a structure using a roller clutch that uses a roller as a plurality of locking members as in the above-described embodiments, but as a plurality of locking members. The present invention can also be applied to a structure using a cam type that uses a cam such as a sprag.

本発明の実施例１を示す半部断面図。FIG. 2 is a half sectional view showing Example 1 of the present invention. 図１のＡ部拡大図。The A section enlarged view of FIG. 保持器のみを取り出して、内径側から見た状態で示す部分斜視図。The partial perspective view which takes out only a holder | retainer and shows it in the state seen from the internal diameter side. 本発明の実施例２を示す半部断面図。Sectional drawing which shows the half part which shows Example 2 of this invention. 同実施例３を示す半部断面図。Sectional sectional drawing which shows the Example 3. FIG. 従来から知られているオルタネータの１例を示す断面図。Sectional drawing which shows one example of the alternator known conventionally. 従来から知られている一方向クラッチ内蔵型プーリ装置の第１例を示す半部断面図。Sectional drawing of the half part which shows the 1st example of the pulley apparatus with a built-in one-way clutch conventionally known. 同第２例を示す断面図。Sectional drawing which shows the 2nd example.

符号の説明Explanation of symbols

１ オルタネータ
２ ハウジング
３ 回転軸
４ 転がり軸受
５ ロータ
６ 整流子
７、７ａ プーリ
８ ボルト
９、９ａ、９ｂ スリーブ
１０、１０ａ、１０ｂ サポート軸受
１１、１１ａ、１１ｂ 一方向クラッチ
１２ 一方向クラッチ用外輪
１３ 凹部
１４ カム面
１５ 一方向クラッチ用内輪
１６ ローラ
１７、１７ａ クラッチ用保持器
１８ 外輪
１９ 内輪
２０ 外輪軌道
２１ 内輪軌道
２２ 玉
２３ａ、２３ｂ シールリング
２４ 環状部材
２５ 無端ベルト
２６ 内輪
２７ 外輪
２８ 軸受用保持器
２９ ころ
３０ 鍔部
３１ 鍔部
３２ 環状部材
３３ カバー
３４ 雌ねじ部
３５ 雄ねじ部
３６ 係合部
３７ 六角孔部
３９ スリーブ小径部
４０ 段差面
４１ 一方向クラッチ用外輪
４２ａ、４２ｂ 鍔部
４３ 円筒状隙間
４４ リム部
４５ ポケット
４６ 凸部
４７ 抑え片
４８ 抑え鍔部
４９ 係合突部
５０ 逃げ溝
５１ 係止溝
５２ 鍔部
５３、５３ａ 第二のシールリング
５４ 芯金
５５ 弾性材
５６ 折れ曲がり部
５７ シールリップ
５８ 通孔
５９ 柱部
６０ 円輪部
６１ 外径側円筒部
６２ 内径側円筒部
６３ 段部
６４ 第二の段部
６５ 段差面
６６ 通孔
６７ 段差面 DESCRIPTION OF SYMBOLS 1 Alternator 2 Housing 3 Rotating shaft 4 Rolling bearing 5 Rotor 6 Commutator 7, 7a Pulley 8 Bolt 9, 9a, 9b Sleeve 10, 10a, 10b Support bearing 11, 11a, 11b One-way clutch 12 One-way clutch outer ring 13 Recess 14 Cam surface 15 Inner ring for one-way clutch 16 Roller 17, 17a Retainer for clutch 18 Outer ring 19 Inner ring 20 Outer ring race 21 Inner ring race 22 Ball 23a, 23b Seal ring 24 Annular member 25 Endless belt 26 Inner ring 27 Outer ring 28 Bearing cage 29 Roller 30 flange 31 flange 32 annular member 33 cover 34 female thread 35 male thread 36 engaging section 37 hexagonal hole 39 sleeve small diameter section 40 stepped surface 41 one-way clutch outer ring 42a, 42b collar 43 cylindrical gap 44 Rim part 45 Pocket 46 Part 47 Holding piece 48 Holding collar 49 Engaging protrusion 50 Escape groove 51 Locking groove 52 Hitting part 53, 53a Second seal ring 54 Core metal 55 Elastic material 56 Bending part 57 Seal lip 58 Through hole 59 Column part 60 Circular ring part 61 Outer diameter side cylindrical part 62 Inner diameter side cylindrical part 63 Step part 64 Second step part 65 Step surface 66 Through hole 67 Step surface

Claims (3)

回転軸の先端部に結合固定自在なスリーブと、このスリーブの周囲にこのスリーブと同心に配置したプーリと、これらスリーブの外周面の軸方向中間部とプーリの内周面の軸方向中間部との間に設け、このプーリが上記スリーブに対し所定方向に相対回転する傾向となる場合にのみ、これらプーリとスリーブとの間での回転力の伝達を自在とする一方向クラッチと、この一方向クラッチを軸方向両側から挟む状態で、上記スリーブの外周面とプーリの内周面との間に設け、このプーリに加わるラジアル荷重を支承しつつこれらスリーブとプーリとの相対回転を自在とした１対のサポート軸受とを備えた一方向クラッチ内蔵型プーリ装置に於いて、上記プーリの内周面及びスリーブの外周面の間部分のうち、少なくとも上記回転軸の基端側と反対側の端部でこの端部側に設けたサポート軸受の転動体よりも軸方向外側に設けられた、その径方向一端部が相手面と摺接するシール部材と、上記プーリの内周面又はスリーブの外周面の軸方向両端部のうち、少なくとも上記回転軸の基端側と反対側の端部で上記シール部材よりも軸方向外側に外れた部分に、全周に亙り径方向に凹んだ状態で形成した段部と、その径方向一端部を上記段部に嵌合させると共に、その径方向他端部を上記スリーブの外周面又はプーリの内周面に摺接若しくは近接対向させた第二のシール部材とを備えた事を特徴とする一方向クラッチ内蔵型プーリ装置。   A sleeve that can be coupled and fixed to the tip of the rotating shaft, a pulley arranged concentrically with the sleeve around the sleeve, an axial intermediate portion of the outer peripheral surface of the sleeve, and an axial intermediate portion of the inner peripheral surface of the pulley A one-way clutch that allows transmission of rotational force between the pulley and the sleeve only when the pulley tends to rotate relative to the sleeve in a predetermined direction. With the clutch sandwiched from both sides in the axial direction, the sleeve is provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley, and the sleeve and the pulley can freely rotate relative to each other while supporting a radial load applied to the pulley. In a pulley apparatus with a built-in one-way clutch provided with a pair of support bearings, at least a portion of the portion between the inner peripheral surface of the pulley and the outer peripheral surface of the sleeve opposite to the base end side of the rotating shaft. A seal member provided on the outer side in the axial direction with respect to the rolling element of the support bearing provided on this end side at the end portion on the side, and an inner peripheral surface or sleeve of the pulley, the radial end portion of which is in sliding contact with the mating surface Of the outer peripheral surface of the outer peripheral surface of the outer peripheral surface of the rotary shaft at least on the opposite side to the base end side of the rotating shaft, the portion that is outside the axial direction of the seal member, and is radially recessed over the entire circumference The step portion formed in step (b) and one end portion in the radial direction are fitted into the step portion, and the other end portion in the radial direction is slidably contacted or closely opposed to the outer peripheral surface of the sleeve or the inner peripheral surface of the pulley. One-way clutch built-in pulley apparatus, characterized by comprising a sealing member. シール部材の径方向外端部を、プーリとスリーブとのうち、プーリ側の部材に固定しており、段部が、上記スリーブの外周面の軸方向両端部のうち、少なくとも回転軸の基端側と反対側の端部で上記シール部材よりも軸方向外側に外れた部分に、全周に亙り径方向内側に凹んだ状態で形成したものであり、第二のシール部材の径方向内端部を上記段部に嵌合させると共に、この第二のシール部材の径方向外端部を上記プーリの内周面に摺接若しくは近接対向させている、請求項１に記載した一方向クラッチ内蔵型プーリ装置。   The radially outer end of the seal member is fixed to the pulley-side member of the pulley and the sleeve, and the stepped portion is at least the base end of the rotating shaft among the axial ends of the outer peripheral surface of the sleeve. The inner end of the second seal member is formed in a state in which the outer end of the second seal member is indented radially inward over the entire circumference at a portion outside the seal member on the outer side in the axial direction. The one-way clutch built-in according to claim 1, wherein a portion is fitted to the step portion, and a radially outer end portion of the second seal member is slidably contacted or closely opposed to the inner peripheral surface of the pulley. Type pulley device. 段部が係止溝であり、第二のシール部材が、芯金と弾性材とで構成され、この弾性材の一部を弾性的に圧縮した状態で上記係止溝に固定したものである、請求項１に記載した一方向クラッチ内蔵型プーリ装置。The step portion is a locking groove, and the second seal member is composed of a core metal and an elastic material, and a part of this elastic material is elastically compressed and fixed to the locking groove. The one-way clutch built-in pulley apparatus according to claim 1.
JP2005139604A 2005-05-12 2005-05-12 One-way clutch built-in pulley device Expired - Fee Related JP3724506B2 (en)

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