JP2000337479A - Roller clutch built-in type pulley device for alternator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability of a roller clutch and to prevent the failure in operation. SOLUTION: A cam surface 17 forming a roller clutch 11 is formed on an outer peripheral surface of an inner ring 15 for roller clutch externally fitted and fixed to an axial intermediate part of a sleeve 8. On the other hand, a cylindrical inner ring track 18 forming a radical roller bearing 9 as a support bearing at one side is directly formed on an outer circumferential surface of the sleeve 8.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a pulley device with a built-in roller clutch for an alternator, which is fixed to an end of a rotating shaft of an alternator which is a generator for an automobile and fixed to an end of a crankshaft of an engine. The alternator is used to drive the alternator by wrapping an endless belt between the drive pulleys.

[0002]

2. Description of the Related Art The structure of an alternator for generating electric power necessary for an automobile using an engine for driving the automobile as a driving source is described in, for example, Japanese Patent Application Laid-Open No. 7-139550. FIG. 4 shows an alternator 1 described in this publication. The rotating shaft 3 is rotatably supported inside the housing 2 by a pair of rolling bearings 4, 4. A rotor 5 and a commutator 6 are provided at an intermediate portion of the rotating shaft 3. A driven pulley 7 is provided at one end (right end in FIG. 4) of the rotating shaft 3 protruding outside the housing 2.
Is fixed. In an assembled state to the engine, an endless belt is stretched over the driven pulley 7, and the rotary shaft 3 is rotatably driven by the crankshaft of the engine.

Conventionally, the driven pulley 7 is generally
What was simply fixed to the rotating shaft 3 was used. On the other hand, in recent years, when the traveling speed of the endless belt is constant or increasing, transmission of power from the endless belt to the rotating shaft is freely performed, and when the traveling speed of the endless belt tends to decrease, Various pulley devices with a built-in roller clutch for an alternator have been proposed and used in part, which enable relative rotation between a driven pulley and a rotating shaft. For example, JP-A-56-101353, JP-A-7-3
No. 17807, No. 8-61443, No. 8-2
Japanese Patent Publication No. 26462, Japanese Patent Publication No. 7-72585, French Patent Publication FR2726059A1, and the like describe a pulley device with a built-in roller clutch for an alternator having the above-described functions.

The pulley devices with a built-in roller clutch described in each of these documents have a sleeve that can be externally fitted and fixed to a rotating shaft of an alternator, and a driven pulley having a cylindrical inner peripheral surface is provided around the sleeve. , Arranged concentrically with this sleeve. A pair of support bearings and a roller clutch are provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley. Of these, support bearings
While supporting the radial load applied to the driven pulley, the relative rotation between the sleeve and the driven pulley is made free.
Also, the roller clutch allows the transmission of the rotational force from the driven pulley to the sleeve only when the driven pulley rotates in a predetermined direction with respect to the sleeve.

The reason for using the pulley device with a built-in roller clutch for an alternator as described above is as follows. For example, when the driving engine is a diesel engine, the rotation angular speed of the crankshaft greatly fluctuates during low rotation such as during idling. As a result, the running speed of the endless belt (not shown), which runs over the drive pulley fixed to the end of the crankshaft, also fluctuates finely. On the other hand, the rotating shaft 3 of the alternator 1, which is rotationally driven by the endless belt via a driven pulley, is connected to the rotating shaft 3 and the inertial mass of the rotor 5 and the commutator 6 (FIG. 4) fixed to the rotating shaft 3. And does not fluctuate so rapidly. Therefore, when the driven pulley is simply fixed to the rotating shaft 3, the endless belt and the driven pulley tend to rub in both directions due to a change 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 driven pulley, so that slippage easily occurs between the endless belt and the driven pulley, or the life of the endless belt is shortened. Or cause The reduction in the life of the endless belt due to the friction between the outer peripheral surface of the driven pulley and the inner peripheral surface of the endless belt also occurs due to repeated acceleration and deceleration during traveling.

Therefore, by using the pulley device with a built-in roller clutch for alternator as the driven pulley as described above, when the running speed of the endless belt is constant or tends to increase, the driven pulley rotates. When the running speed of the endless belt tends to decrease, the relative rotation between the driven pulley and the rotating shaft 3 is made freely. That is, when the running speed of the endless belt tends to decrease, the rotational angular speed of the driven pulley is made slower than the rotational angular speed of the rotating shaft 3 so that the contact portion between the endless belt and the driven pulley is strong. Prevent rubbing. In this way, the direction of the stress acting on the rubbed portion between the driven pulley and the endless belt is kept constant, slippage occurs between the endless belt and the driven pulley, or the life of the endless belt is shortened. To prevent

[0007] As a pair of support bearings constituting a pulley device with a built-in roller clutch for an alternator as described above, a radial roller bearing or a radial ball bearing has been generally used conventionally. When a pair of radial roller bearings are used as the pair of support bearings, they can be sufficiently supported even when a large radial load is applied to the driven pulley. However, in the case of the radial roller bearing, since a thrust load applied to the driven pulley cannot be supported, it is necessary to provide a separate member such as a thrust washer to support the thrust load. However, providing such a separate member not only causes trouble in assembling work and parts management, but also ensures durability of the grease regardless of heat generated in the sliding friction portion. Expensive grease having excellent heat resistance must be used. In order to avoid an increase in cost due to such a cause, one of the pair of support bearings should be a deep groove type radial ball bearing capable of supporting both a radial load and a thrust load. preferable.

In view of such circumstances, Japanese Unexamined Patent Application Publication No. Hei 8-226462 among the above-mentioned documents discloses that a pair of support bearings each including one radial roller bearing and one radial ball bearing are used. Is described. In the case of the alternator roller clutch built-in type pulley device described in this publication, a radial roller bearing is used as one of the support bearings, so that a relatively large radial load can be supported as a whole. In addition, since a radial ball bearing is used as the other support bearing, a thrust load applied to the driven pulley can be freely supported. Therefore, there is no need to provide a separate member for supporting the thrust load as described above.

[0009]

The roller clutches constituting the alternator built-in roller clutch type pulley device as described above are each formed of a cylindrical member existing between a cam surface and a cylindrical surface constituting the roller clutch. The locked state of the roller clutch is realized by making a plurality of rollers bite into a part of the space having a narrow width in the diameter direction. In the case of the conventional structure described in JP-A-8-226462, the cam surface constituting the roller clutch as described above is formed directly on the outer peripheral surface of the sleeve. However, since such a sleeve is usually formed by forging a round bar or a round tube made of steel, it is difficult to improve the surface roughness of the cam surface formed on the outer peripheral surface of the sleeve. . For this reason, when the cam surface having a rough surface and the rolling surfaces of the plurality of rollers come into contact with each other at the time of the locking, a local high surface pressure may be generated at the contact portions on these two surfaces. In such a case, the rolling surface of each roller and the cam surface are liable to be easily damaged, such as peeling, and the life of the roller clutch is disadvantageously shortened.

On the other hand, the cam surface forming the roller clutch and the inner raceways forming the pair of support bearings are separate bodies formed by subjecting a bearing steel plate to deep drawing or the like. A pulley device with a built-in roller clutch for an alternator, which is formed on the outer peripheral surface of an inner ring and in which each of these separate inner rings is externally fitted and fixed to the sleeve, is also conventionally known. In the case of such a conventional structure, since the cam surface is formed in the process of subjecting the plate material to deep drawing or the like, not only is it easy to form the cam surface, but also the surface roughness of the cam surface Is also easy to improve. Therefore, the above-described inconvenience does not occur.

However, in the case of the conventional structure as described above, since the inner raceway constituting the support bearing is also formed on the outer peripheral surface of the separate inner race, the following inconvenience occurs. That is, the separate inner ring forming the inner ring raceway of the support bearing is externally fitted and fixed to the outer peripheral surface of the above-described sleeve by interference fitting, for example, for the purpose of facilitating the assembling work. For this reason, the amount of elastic deformation in the diameter direction of the inner ring changes according to the size of the interference, and the diameter of the inner ring raceway formed on the outer peripheral surface of the inner ring changes. In particular,
In the case of the inner ring made of a plate material as described above, since the wall thickness in the diameter direction is small, the diameter of the inner ring raceway easily changes according to the size of the interference, and the variation in the amount of change also increases. Therefore, it is difficult to regulate the diameter of the inner raceway to an appropriate value.

If the radial gap (the internal gap in the diametric direction) of the support bearing greatly varies based on such a variation, the width dimension in the diametric direction between the cylindrical surface and the cam surface constituting the roller clutch becomes large. , Greatly differ from the desired value. In such a case, the amount of displacement of the plurality of rollers in the circumferential direction largely varies, and as a result, the pressing force of the elastic member pressing each of the rollers varies. Also, when the roller clutch is to be locked, it is difficult to lock the roller clutch (when the pressing force is too small) or when the roller surface slides between the cylindrical surface and the cam surface and the rollers at the time of overrun which is unlocked. There is a possibility that inconvenience such as abnormal heating easily occurring at the contact portion (when the pressing force is excessive) is caused. In addition, when the width in the diametric direction between the cylindrical surface and the cam surface is increased, there is a possibility that the respective rollers may easily ride on the edge of the concave portion forming the cam surface, and may cause inconvenience. . The roller clutch built-in pulley device for an alternator of the present invention uses a radial ball bearing and a radial roller bearing as a pair of support bearings, and has been invented to realize a structure that does not cause the above-described inconvenience. Things.

[0013]

According to the present invention, there is provided a pulley device with a built-in roller clutch for an alternator according to the present invention described in Japanese Patent Application Laid-open No.
As in the conventional structure described in JP-A-226462,
A sleeve which can be fitted and fixed on the rotating shaft of the alternator, a driven pulley disposed concentrically with the sleeve around the sleeve, an axially intermediate portion of an outer peripheral surface of the sleeve and an axially intermediate portion of an inner peripheral surface of the driven pulley. A roller clutch provided between the driven pulley and the sleeve only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction. Provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley at a position sandwiching the roller clutch from both axial sides,
There is provided a pair of support bearings that allow the sleeve and the driven pulley to freely rotate while supporting the radial load applied to the driven pulley. One of the pair of support bearings is a radial roller bearing, and the other support bearing is a deep groove type radial ball bearing capable of supporting a thrust load in both directions in addition to a radial load. In particular, in the alternator roller clutch built-in type pulley device of the present invention, the cam surface constituting the roller clutch is formed on the outer peripheral surface of the roller clutch inner ring externally fixed to the axially intermediate portion of the sleeve. At the same time, a cylindrical inner raceway constituting the radial roller bearing is formed directly on the outer peripheral surface of the sleeve.

[0014]

In the pulley apparatus with a built-in roller clutch for an alternator according to the present invention, the cam surface forming the roller clutch is formed on the outer peripheral surface of the roller clutch inner ring formed separately from the sleeve. . Such an inner ring for a roller clutch can be easily formed by subjecting a steel plate to deep drawing or by drawing a steel material into a cylindrical material, and furthermore, forming the cam surface after forming. Good surface roughness (smooth surface). For this reason, even when the cam surface and the rolling surfaces of the plurality of rollers come into contact with each other when the roller clutch is locked, local high surface pressure is not generated at the contact portions on these two surfaces. For this reason, damage such as peeling can be less likely to occur between the rolling surface of each roller and the cam surface. Therefore, the durability of the roller clutch can be improved.

Further, in the case of the present invention, the cylindrical inner raceway constituting the radial roller bearing as one of the support bearings is not formed on the outer peripheral surface of a separate inner race, but is formed directly on the outer peripheral surface of the sleeve. ing. As described above, it is easy to directly form the cylindrical inner raceway on the outer peripheral surface of the sleeve, and it is also easier to regulate the diameter of the inner raceway to an appropriate value. Therefore, unlike the conventional structure described above, the inner ring raceway is formed on the outer peripheral surface of a separate inner ring, and the inner ring is fixed to the outer peripheral surface of the sleeve by external fitting with a tight fit. The gap does not vary greatly, and this radial gap can be regulated to an appropriate value. Therefore, based on the fact that this radial gap varies greatly,
During operation, the width dimension in the diameter direction between the cylindrical surface and the cam surface constituting the roller clutch does not vary greatly. Therefore, the width dimension becomes excessively large, making it difficult for the roller clutch to be locked, or the width dimension becomes excessively small, causing abnormal heat generation in the sliding portion during overrun, and further increasing. As a result, there is no inconvenience that a plurality of rollers ride on the edge of the concave portion forming the cam surface.

In the case of the present invention, the inner raceway of the deep groove type which constitutes the radial ball bearing which is the other support bearing may be formed directly on the outer peripheral surface of the sleeve, or may be formed on the outer peripheral surface of a separate inner race. And the inner ring may be externally fitted and fixed to the outer peripheral surface of the sleeve. The reason for this is that the separate inner ring for forming the deep groove type inner ring raceway has a relatively large wall thickness in the diametrical direction, so that even when the outer ring is fixed to the sleeve by tight fitting, it is of a degree normally employed. This is because the diameter of the inner raceway of the deep groove type does not change so much at the interference. That is, in the case of the radial ball bearing, whether the deep groove type inner ring raceway is formed directly on the outer peripheral surface of the sleeve, or formed on the outer peripheral surface of a separate inner ring, The diameter dimension of the raceway can be regulated to an appropriate value, and the inconvenience such that the radial clearance of the radial ball bearing greatly varies does not occur.

[0017]

FIG. 1 shows a first embodiment of the present invention. The alternator roller clutch built-in type pulley device of the present embodiment has a sleeve 8 which can be externally fitted and fixed to the rotating shaft 3 (see FIG. 4) of the alternator 1. A driven pulley 7 a is arranged around the sleeve 8 concentrically with the sleeve 8. A pair of support bearings, a radial roller bearing 9 and a radial ball bearing 10, and a roller clutch 11 are provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a. Of these, the radial roller bearing 9 and the radial ball bearing 10
Allows the relative rotation between the sleeve 8 and the driven pulley 7a while supporting the radial load applied to the driven pulley 7a. In particular, the radial ball bearing 10 is of a deep groove type and is capable of supporting a thrust load applied to the driven pulley 7a. Only when the driven pulley 7a tends to rotate relative to the sleeve 8 in a predetermined direction, the roller clutch 11
The transmission of the rotational force from the shaft to the sleeve 8 can be made freely.

That is, in the pulley device with a built-in roller clutch for an alternator of the present embodiment as described above, the sleeve 8 is used.
Is formed into a cylindrical shape by forging a quenching-hardenable steel material such as S53C or S55C, and is externally fitted and fixed to the end of the rotating shaft 3 of the alternator 1. Thus, it is rotatable with the rotating shaft 3. For this reason, in the illustrated example, a screw hole 12 is formed in the inner peripheral surface of the middle portion of the sleeve 8 near the tip (the portion near the left end in FIG. 1), and the screw hole 12 and the tip of the rotating shaft 3 are formed. An external thread portion provided on the outer peripheral surface of the portion can be screwed freely. A cylindrical fitting hole 13 is formed in the inner peripheral surface of the base half (the right half in FIG. 1) of the sleeve 8. Can be freely fitted inside without rattling. Further, a locking hole portion 14 having a hexagonal cross section is formed on the inner peripheral surface of the distal end portion of the sleeve 8.
4, the tip of a tool such as a hexagon wrench can be freely locked. Note that the structure in which the sleeve 8 and the rotating shaft 3 are combined so as not to rotate relative to each other may employ other structures such as spline engagement, non-circular engagement, and key engagement.

On the other hand, the outer peripheral surface of the driven pulley 7a has a cross-sectional shape extending in the width direction and has a corrugated shape so that a part of an endless belt called a poly-V belt can be passed around. or,
The inner peripheral surface of the driven pulley 7a is formed in a simple cylindrical shape over the entire length. The roller clutch 11 is provided at an axially intermediate portion of a space existing between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a. The radial roller bearing 9 and the radial ball bearing 10 are arranged at positions sandwiching the roller bearings from both sides in the axial direction. In the case of the illustrated example, the radial roller bearing 9 is disposed at a distal end portion of the space, and the radial ball bearing 10 is disposed at a proximal end portion of the space.

Further, in order to constitute the roller clutch 11, an inner ring 15 for the roller clutch is fixed to the outer peripheral surface of the intermediate portion of the sleeve 8 by tight fitting. The inner ring 15 for the roller clutch is formed into a cylindrical shape as a whole by subjecting a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415 to a deep drawing process. Has been given. A plurality of recesses 16 called ramps are formed on the outer peripheral surface of the roller clutch inner ring 15 at regular intervals in the circumferential direction, so that the outer peripheral surface is a cam surface 17. The sleeve 8 can also be formed by performing a drawing process on a cylindrical material made of steel as described above. Also, in the case of the present embodiment in which the roller clutch inner ring 15 is formed by the deep drawing or drawing process, the cam surface 17 can be easily formed on the outer peripheral surface of the roller clutch inner ring 15, and the cam after molding is formed. The surface roughness of the surface 17 can be made relatively small (smooth surface). The inner raceway 18 constituting the radial roller bearing 9 is formed directly on the outer peripheral surface of the distal end of the sleeve 8. That is, in such an inner raceway 18, after forming the outer peripheral surface of the distal end portion of the sleeve 8 into a cylindrical surface by the forging process described above, the outer peripheral surface of the distal end portion is subjected to quenching processing by high frequency and grinding. It is formed by.

On the other hand, an outer ring 19 is provided on the inner peripheral surface of the driven pulley 7a near the front end of the intermediate portion (the portion near the left end in FIG. 1).
The inner fit is fixed by interference fit. This outer ring 19
It functions not only as an outer ring of the roller clutch 11 but also as an outer ring of the radial roller bearing 9, and is also formed by pressing a hard metal plate such as bearing steel or a carburized steel plate such as SCM415. Are formed in a cylindrical shape as a whole. Inward flange-shaped flanges 20 are formed on both axial edges of the outer ring 19, respectively. The inner peripheral surface of the outer ring 19 is a mere cylindrical surface over substantially the entire length except for the flange portions 20 and 20 formed at both ends.

The roller clutch 11 includes a base half (the right half in FIG. 1) of the outer ring 19 and the roller clutch inner ring 15. That is, between the inner peripheral surface of the base half portion of the outer race 19 and the outer peripheral surface of the inner race 15 for the roller clutch, a cage 21 for a clutch formed of a synthetic resin into a cylindrical shape, and a plurality of rollers 22 each comprising And a spring (not shown). The clutch retainer 21 has a plurality of projections 2 formed on its inner peripheral surface.
3 and 23 are the cam surfaces 17 of the roller clutch inner ring 15.
To prevent the rotation relative to the roller clutch inner ring 15. Since the basic structure and operation of the roller clutch 11 are well known in the art, detailed illustration and description are omitted.

The radial roller bearing 9 includes a first half (left half in FIG. 1) of the outer ring 19 and an inner raceway 18 formed on the outer peripheral surface of the distal end of the sleeve 8. . That is, between the inner peripheral surface of the first half portion of the outer ring 19 and the inner raceway 18, a cage 24 for a roller bearing formed of a synthetic resin in a cage shape and rolling by the cage 24 for the roller bearing. A plurality of rollers 25 which are freely held are provided. Further, the inner peripheral surface of the distal end portion of the outer ring 19 and the sleeve 8
Is closed by a seal ring 26. The seal ring 26 is composed of a metal core 27 and an elastic material 28, and is fitted and supported on the inner peripheral surface of the distal end portion of the outer ring 19 in a state where the outer diameter of the elastic material 28 is elastically reduced. ing. The distal edges of the plurality of seal lips provided on the elastic member 28 are slid or abutted on the inner peripheral surface of the distal end of the sleeve 8 and the inner surface of the flange 20. When the roller clutch and the radial roller bearing 9 are assembled as described above, the clutch retainer 21 and the bearing retainer 24 are separated from the flange 20 provided at the base end of the outer ring 19. It is arranged between the side surface and the side surface of the metal core 27 constituting the seal ring 26, and is prevented from being displaced in the axial direction.

The radial ball bearing 10 includes a ball bearing outer ring 30 having a deep groove type outer ring track 29 locked on an inner peripheral surface thereof;
A ball bearing inner ring 32 having a deep groove type inner raceway 31 formed on the outer peripheral surface; a plurality of balls 33 rotatably provided between the outer raceway 29 and the inner raceway 31; And a ball bearing retainer 34 made of synthetic resin which is movably held. In such a radial ball bearing 10, the outer ring 30 for ball bearing is internally fitted and fixed to the inner peripheral surface of the base end (the right end in FIG. 1) of the driven pulley 7a by interference fitting. The outer peripheral surface of the sleeve 8 is fixed between the inner peripheral surface of the proximal end portion of the driven pulley 7 a and the outer peripheral surface of the proximal end portion of the sleeve 8.

In the case of the illustrated example, the inner race 32 for the ball bearing is used.
A small-diameter step portion 35 provided at the base end of the sleeve 8,
For example, after externally fitting with a clearance fit, the sleeve 8 is clamped between the step surface 36 of the small-diameter stepped portion 35 and a caulking portion 37 formed on the outer peripheral edge portion of the base end of the sleeve 8.
It is fixed against. In the case of this example, the caulking section 37
Is formed by plastically deforming a plurality of locations (for example, 4 to 8 locations) in the circumferential direction of the outer peripheral edge portion of the base end portion of the sleeve 8 toward the end face of the ball bearing inner ring 32 in the diametrically outward direction. I have. In the illustrated example, a clearance groove 38 is formed on the inner diameter side portion of the caulking portion 37 over the entire circumference. The relief groove 38 is for preventing the inner diameter of the fitting hole 13 provided at the center of the sleeve 8 from changing when the caulking portion 37 is formed. In order to improve the fixing force of the caulking portion 37, the caulking portion 37 may be formed by plastically deforming the outer peripheral edge of the base end of the sleeve 8 over the entire circumference.

In the state where the radial ball bearing 10 is assembled as described above, the outer end of the space existing between the inner peripheral surface of the outer race 30 for ball bearings and the outer peripheral surface of the inner race 32 for ball bearings. The opening (right end in FIG. 1) is sealed by a seal ring 39 locked on the inner peripheral surface of the outer end of the outer race 30 for a ball bearing. That is, in the case of the present example, the roller clutch 11, the radial roller bearing 9, and the radial ball bearing 1 are formed by the seal ring 39 and the seal ring 26 described above.
In addition to preventing intrusion of foreign matter such as muddy water into the internal space, the grease sealed in the internal space is prevented from leaking to the outside.

In the case of the pulley device with a built-in roller clutch for an alternator of the present embodiment constructed as described above, the rotation speed of the driven pulley 7a over which the endless belt is stretched is controlled by the action of the low clutch 11 so that the alternator 1 The torque is transmitted from the driven pulley 7a to the rotary shaft 3 only when the rotational speed is equal to or higher than the rotational speed of the sleeve 8 fixed to the rotary shaft 3 (see FIG. 4). Conversely, when the rotation speed of the driven pulley 7a is lower than the rotation speed of the sleeve 8,
The connection between the driven pulley 7a and the sleeve 8 is disconnected to prevent an unnecessary (braking direction) force from being applied to the endless belt. In addition, one radial roller bearing 9 and one radial ball bearing 10 are used as a pair of support bearings. Therefore, not only can the relatively large radial load applied to the driven pulley 7a be sufficiently supported by the radial roller bearing 9, but also the thrust load in both directions applied to the driven pulley 7a can be supported by the radial ball bearing 10. it can.

Particularly, in the case of this embodiment, the cam surface 17 constituting the roller clutch 11 is formed on the outer peripheral surface of the roller clutch inner race 15 formed separately from the sleeve 8. As described above, such an inner ring 15 for a roller clutch is used.
Can be easily made by subjecting a steel plate to deep drawing, and the surface roughness of the cam surface 17 after forming can be made relatively small. For this reason, even when the cam surface 17 and the rolling surfaces of the plurality of rollers 22 contact each other when the roller clutch 11 is locked, local high surface pressure does not occur at the contact portion. . For this reason, damage such as peeling can be less likely to occur between the rolling surface of each roller 22 and the cam surface 17, and
The durability of the roller clutch 11 can be improved.

Further, in the case of this embodiment, the cylindrical inner raceway 18 constituting the radial roller bearing 9 as one of the support bearings is not formed on the outer peripheral surface of a separate inner ring, but is formed on the outer peripheral surface of the sleeve 8. Formed directly. As described above, it is easy to form the cylindrical inner raceway 18 on the outer peripheral surface of the sleeve 8, and it is also easy to regulate the diameter of the inner raceway 18 to an appropriate value. Therefore, unlike the conventional structure described above, the inner ring raceway 18 is formed on the outer peripheral surface of a separate inner ring, and this inner ring is externally fixed to the outer peripheral surface of the sleeve 8 by interference fit. The radial gap of No. 9 does not vary greatly, and this radial gap can be regulated to an appropriate value. And it becomes possible to regulate this radial gap to a small value. For this reason, the radial dimension between the inner peripheral surface of the outer race 19 and the cam surface 17 does not greatly vary with the large variation of the radial gap. Therefore, if the width dimension becomes excessively large, the roller clutch 11 becomes difficult to lock, or becomes excessively small, causing abnormal heat generation in the sliding portion at the time of overrun. There is no inconvenience such as that the roller 22 rides on the edge of the concave portion 16 constituting the cam surface 17.

In the case of this embodiment, the inner raceway 31 of the deep groove type constituting the radial ball bearing 10 which is the other support bearing.
Are formed on the outer peripheral surface of the ball bearing inner ring 32 separate from the sleeve 8. However, in the case of this example, since the ball bearing inner ring 32 is fitted over the outer peripheral surface of the sleeve 8 with a clearance fit, the inner ring raceway 31 formed on the outer peripheral surface of the ball bearing inner ring 32 is formed. As a result, the radial clearance of the radial ball bearing 10 does not increase. Even if the ball bearing inner ring 32 is externally fitted and fixed to the outer peripheral surface of the sleeve 8 by interference fit, the deep groove type inner ring raceway 31 may be used.
Since the thickness in the diameter direction of the ball bearing inner ring 32 in which the inner ring raceway 31 is formed is large, the diameter of the inner ring raceway 31 does not change so much as to be a problem with the normally adopted interference. Therefore, as in the present example, the deep groove type inner raceway 31 is
Even if it is formed on the outer peripheral surface of the ball bearing inner ring 32 separate from the sleeve 8, the diameter of the deep groove type inner ring raceway 31 can be regulated to an appropriate value, and if the radial gap of the radial ball bearing 10 greatly varies. The inconvenience mentioned does not occur. The inner raceway 31 as described above may be formed directly on the outer peripheral surface of the sleeve 8.

Next, FIG. 2 shows a second embodiment of the present invention.
An example is shown. In the case of this example, a spline hole 40 is formed in the inner diameter side portion of the distal end of the sleeve 8a, and a spline shaft provided at the distal end of the assembling tool is freely engageable with the spline hole 40. In the case of this example, since the engagement between the sleeve 8a and the assembling tool is spline engagement, a sufficient torque can be applied to the sleeve 8a even if the pitch circle diameter of the spline hole 40 is reduced. . Therefore, in the case of this example, the spline hole 40
The diameter of the circumscribed circle with respect to the groove bottom of the screw hole 12 and the fitting hole 1 provided in the intermediate portion and the base end of the sleeve 8a
3 is smaller than the inner diameter. Accordingly, in the case of the present embodiment, the outer peripheral surface of the sleeve 8a is formed in a single cylindrical shape over the entire length, thereby reducing the processing cost of the sleeve 8a. Further, in the case of this example, the ball bearing inner race 32 externally fitted to the outer peripheral surface of the base end portion of the sleeve 8a is a base of the roller clutch inner race 15 externally fitted and fixed to the axially intermediate portion of the sleeve 8a by interference fit. It is sandwiched between an end edge (the right end edge in FIG. 2) and a retaining ring (C ring) 41 which is locked on the outer peripheral surface of the base end portion of the sleeve 8a, thereby positioning in the axial direction.

Further, in the case of this embodiment, the formation of a flange at the base end (the right end in FIG. 2) of the outer ring 19a fitted and fixed to the driven pulley 7a is omitted, and the manufacturing cost of the outer ring 19a is reduced. And easy assembling work. In addition, the omission of the formation of the flange at the base end of the outer ring 19a has resulted in the base end face of the clutch retainer 21 (the right end face in FIG. 2).
The inner side surface of the inner ring 32 of the ball bearing inner ring 32 (FIG.
(Left end face of the clutch). The clutch retainer 21 is prevented from being displaced toward the radial ball bearing 10 by being opposed to the outer diameter side portion.

In the case of the present embodiment, the seal ring 42 for sealing the front end opening of the space existing between the inner peripheral surface of the driven pulley 7a and the outer peripheral surface of the sleeve 8a is provided at the distal end of the outer ring 19a. It is provided on the outer side (left side in FIG. 2) of the flange portion 20 provided on the left side in FIG. This seal ring 42
Is a metal core 43 having an L-shaped cross section and formed entirely in an annular shape;
And an elastic member 44 attached to the core bar 43. Such a seal ring 42 press-fits the core metal 43 into the inner peripheral surface of the distal end portion of the driven pulley 7a and fixes it inside. It is in sliding contact with the outer peripheral surface of the sleeve 8a over the circumference. Other configurations and operations are the same as those of the above-described first example.

FIG. 3 shows a third embodiment of the present invention.
An example is shown. In the case of this example, a small-diameter stepped portion 35a is formed on the outer peripheral surface of the sleeve 8a from the middle portion in the axial direction to the base end (the right end in FIG. 3). The roller clutch inner ring 15 and the ball bearing inner ring 32 are externally fitted and fixed to the small-diameter stepped portion 35a. Further, in this state, the roller clutch inner ring 15 and the ball bearing inner ring 32 are moved between the step surface 36 of the small diameter step 35a and the retaining ring 41 locked to the base end of the small diameter step 35a. To achieve positioning in the axial direction. Other configurations and operations are
This is similar to the case of the second example described above.

[0035]

The pulley apparatus with a built-in roller clutch for an alternator according to the present invention is constructed and operated as described above. Therefore, in the structure using a radial ball bearing and a radial roller bearing as a pair of support bearings. Thus, it is possible to improve the durability of the roller clutch and prevent the occurrence of malfunction.

[Brief description of the drawings]

FIG. 1 is a half sectional view showing a first example of an embodiment of the present invention.

FIG. 2 is a half sectional view showing the second example.

FIG. 3 is a half sectional view showing the third example.

FIG. 4 is a sectional view showing an example of a conventionally known alternator.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Alternator 2 Housing 3 Rotating shaft 4 Rolling bearing 5 Rotor 6 Commutator 7, 7a Driven pulley 8, 8a Sleeve 9 Radial roller bearing 10 Radial ball bearing 11 Roller clutch 12 Screw hole 13 Fitting hole 14 Locking hole 15 Roller clutch inner ring 16 Recess 17 Cam surface 18 Inner ring track 19, 19a Outer ring 20 Flange 21 Clutch retainer 22 Roller 23 Projection 24 Roller bearing retainer 25 Roller 26 Seal ring 27 Core metal 28 Elastic material 29 Outer ring track 30 Ball bearing outer ring 31 Inner ring raceway 32 Ball bearing inner ring 33 Ball 34 Ball bearing retainer 35, 35a Small diameter stepped portion 36 Stepped surface 37 Caulking portion 38 Relief groove 39 Seal ring 40 Spline hole 41 Stop ring 42 Seal ring 43 core Gold 44 elastic material

Claims (1)

[Claims] 1. A sleeve which can be externally fitted and fixed to a rotating shaft of an alternator, a driven pulley disposed around the sleeve and concentric with the sleeve, an axially intermediate portion of an outer peripheral surface of the sleeve, and an inner periphery of the driven pulley. Provided between the driven pulley and the sleeve only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction. A roller clutch, provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley at a position sandwiching the roller clutch from both sides in the axial direction, and supporting the radial load applied to the driven pulley while supporting the sleeve and the driven pulley. And a pair of support bearings that allow relative rotation with respect to one another. One of these support bearings is a radial roller bearing, and the other is a radial roller bearing. In a pulley device with a built-in roller clutch for an alternator using a support bearing as a radial ball bearing, the cam surface constituting the roller clutch is fixed to the outer peripheral surface of a roller clutch inner ring which is externally fitted and fixed to the axially intermediate portion of the sleeve. A pulley device with a built-in roller clutch for an alternator, wherein the cylindrical inner raceway constituting the radial roller bearing is formed directly on the outer peripheral surface of the sleeve.