JP2003090415A - Pulley device with built-in roller clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a structure capable of restraining frictional heat and worn powder generated at overrunning of a roller clutch 10 and exhibiting enhanced durability. SOLUTION: Ball bearings 25 are used as a pair of supporting bearings provided between an inner peripheral surface of a driven pulley 7a and an outer peripheral surface of a sleeve 24. A holder 37 for the clutch is prevented from being displaced along an axial direction by axial engagement of both end surfaces 42 of the holder 37 for the clutch installed in the roller clutch 10 with axially inner end surfaces of holders 40 for the bearing installed in the ball bearings 25. With this structure, friction by axial deformation is restrained and the purpose is attained.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is used, for example, as a driven pulley fixed to the end of a rotary shaft of an alternator, which is a generator for automobiles, or a drive pulley fixed to the end of a crankshaft of an automobile engine. The present invention relates to an improvement of a pulley device with a built-in roller clutch for a belt transmission device of an engine accessory.

[0002]

2. Description of the Related Art A structure of an alternator for generating electric power required for an automobile using an automobile driving engine as a drive source is described in, for example, Japanese Patent Application Laid-Open No. 7-139550. FIG. 8 shows the alternator 1 described in this publication. The rotating shaft 3 is rotatably supported inside the housing 2 by a pair of rolling bearings 4 and 4. A rotor 5 and a commutator 6 are provided in the middle of the rotary shaft 3. The driven pulley 7 is attached to a portion of one end of the rotary shaft 3 (the right end in FIG. 8) protruding outside the housing 2.
Is fixed. In the assembled state to the engine, an endless belt is stretched over the driven pulley 7 so that the crankshaft of the engine can drive the rotary shaft 3 to rotate.

Conventionally, the driven pulley 7 has generally been
The one simply fixed to the rotary shaft 3 was used. On the other hand, in recent years, when the traveling speed of the endless belt is constant or tends to increase, it is possible to freely transmit power from the endless belt to the rotating shaft, and when the traveling speed of the endless belt tends to decrease, Various types of pulley devices with a built-in roller clutch that allow the pulley and the rotary shaft to freely rotate relative to each other have been proposed and are partially used. For example, JP-A-56-
No. 101353, JP-A-7-317807,
No. 8-61443, No. 8-226462,
Japanese Patent Publication No. 7-72585, French Patent Publication FD2
726059A1 and the like describe a roller clutch built-in type pulley device having the above-described function. Further, in part, such a pulley device with a built-in roller clutch is actually used.

FIG. 9 shows, of these, Japanese Patent Application Laid-Open No. 8-226462.
2 shows a pulley device with a built-in roller clutch disclosed in Japanese Patent Publication No. This pulley device with a built-in roller clutch has a sleeve 8 that can be externally fitted and fixed to the rotary shaft 3 of the alternator 1 (FIG. 8). Then, the driven pulley 7a around the sleeve 8 is arranged concentrically with the sleeve 8. A pair of support bearings 9 and 9 and a roller clutch 10 are provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a. Of these, the support bearings 9 and 9 are roller bearings that support the radial load applied to the driven pulley 7a and allow relative rotation between the sleeve 8 and the driven pulley 7a. Further, the roller clutch 10 allows the rotational force to be transmitted from the driven pulley 7a to the sleeve 8 only when the driven pulley 7a tends to rotate relative to the sleeve 8 in a predetermined direction.

On the outer peripheral surface of the intermediate portion of the inner ring 11 which constitutes the roller clutch 10 and is externally fitted and fixed to the sleeve 8,
A plurality of concave portions 12 called ramp portions are formed at equal intervals in the circumferential direction, and the outer peripheral surface of the intermediate portion serves as a cam surface 13. The outer peripheral surfaces of both ends of the inner ring 11 are inner ring raceways 14, 14 for the support bearings 9, 9.
On the other hand, since the roller clutch 10 is configured,
The inner peripheral surface of the outer ring 15 fitted and fixed to the driven pulley 7a is a simple cylindrical surface over almost the entire length. In addition, the inner ring 11 and the outer ring 15 together with the roller clutch 10
The plurality of rollers 16, 16 constituting the above are supported by the clutch holder 17 so as to be rollable and slightly displaceable in the circumferential direction.

For example, FIG. 10 shows an example of a conventionally known structure of the roller clutch constructed as described above. Inner ring 1 that constitutes this roller clutch 10
1 is called a ramp portion at a plurality of locations on the outer peripheral surface of the intermediate portion,
The recesses 12, 12 that become larger in depth toward the one end side in the circumferential direction (left side in FIG. 10) are formed in the axial direction of the inner ring 11 at equal intervals in the circumferential direction. The surface is the cam surface 13. This inner ring 11
Between the outer peripheral surface of the intermediate portion of the
A cylindrical gap 18 is formed. Among the dimensions of the cylindrical gap 18, the width dimension of the outer ring 15 in the diametrical direction is larger than the outer diameter of each roller 16 in the portions corresponding to the recesses 12, 12. The outer diameter of each roller 16 is large and smaller than the outer diameter of each of the rollers 16 in the recesses 12, 12.

The clutch holder 17 constituting the roller clutch 10 is formed into a basket-like cylindrical shape by injection molding synthetic resin. The clutch retainer 17 is arranged inside the outer ring 15, and the convex portions 19 and 19 formed on the inner peripheral surface are engaged with the respective concave portions 12 and 12 formed on the outer peripheral surface of the inner ring 11. As a result, the inner ring 11 is mounted so as not to rotate relative to it. The plurality of rollers 16 are used for the clutch holder 17 as described above.
It is held inside the pockets 20, 20 formed in the above so as to be capable of rolling and slightly displacing in the circumferential direction. In addition, the pillar portions 21 and 2 constituting the clutch holder 17 as described above.
1 and the rollers 16 are provided with springs 22 and 22, which are the same number of elastic members as the rollers 16, and the rollers 16 are oriented in the direction in which the recesses 12 and 12 become shallower. In the same direction (rightward in FIG. 10) with respect to the circumferential direction,
It is pressed elastically. Generally, each of the springs 22,
Reference numeral 22 is a leaf spring made of stainless steel or spring steel formed by folding a strip-shaped spring plate back into a U-shape or a M-shape, or a synthetic resin spring integrally formed with the clutch retainer 17.

The roller clutch 10 constructed as described above.
Between the driven pulley 7a in which the outer ring 15 is fitted and fixed and the rotary shaft 3 (FIG. 9) that rotates together with the inner ring 11,
Only the rotational force in a predetermined direction is transmitted. For example, in FIG. 10, assuming that the inner ring 11 is fixed and only the outer ring 15 rotates,
When the outer ring 15 rotates counterclockwise in the figure,
Based on the force received by the rollers 16 from the inner peripheral surface of the outer ring 15, the recesses 12, 12 tend to be displaced toward the deepened side against the elasticity of the springs 22, 22. Then, each of the rollers 16 has the cylindrical gap 18
The inside of the outer ring 15 and the inner ring 11 become rollable.
There is a so-called overrun state in which torque is not transmitted between and. On the contrary, when the outer ring 15 rotates clockwise in FIG. 10, the rollers 16 receive the force from the inner peripheral surface of the outer ring 15 and the elastic forces of the springs 22, 22 as shown in FIG. As shown by the chain line, the recesses 12, 12 bite into the shallower side in a wedge shape to integrally connect the outer ring 15 and the inner ring 11 and rotate between the outer ring 15 and the inner ring 11. It is in a so-called locked state in which the force can be freely transmitted.

The reason why the roller clutch built-in type pulley device having the above-mentioned structure is used for the alternator is as follows. First, the first reason is to extend the life of the endless belt. For example, when the drive engine is a diesel engine or a direct injection gasoline engine, the rotational angular velocity of the crankshaft fluctuates greatly during low rotation such as idling. As a result, the traveling speed of the endless belt wound around the drive pulley also changes finely. On the other hand, the rotating shaft 3 of the alternator which is rotationally driven by the endless belt via the driven pulley.
Due to the inertial mass of the rotating shaft 3 and the rotor or the like fixed to the rotating shaft 3, does not change so rapidly. Therefore, when the driven pulley is simply fixed to the rotary shaft, the endless belt and the driven pulley tend to rub in both directions as the rotational angular velocity of the crankshaft changes. As a result, the stress in different directions is repeatedly applied to the endless belt that rubs against the driven pulley, and slippage easily occurs between the endless belt and the driven pulley,
Or, it may cause the life of the endless belt to be shortened.

Therefore, by using the above roller clutch built-in type pulley device as such a driven pulley,
When the traveling speed of the endless belt is constant or tends to increase, the rotational force can be freely transmitted from the driven pulley to the rotary shaft 3, and conversely, when the traveling speed of the endless belt tends to decrease. The relative rotation between the driven pulley and the rotary shaft 3 is freely made. That is, when the traveling speed of the endless belt tends to decrease, the rotational angular velocity of the driven pulley is set to be slower than the rotational angular velocity of the rotating shaft 3 so that the contact portion between the endless belt and the driven pulley becomes strong. Prevent rubbing against each other. In this way, the direction of the stress acting on the rubbing portion between the driven pulley and the endless belt is made constant, slippage occurs between the endless belt and the driven pulley, or the life of the endless belt is shortened. Prevent doing.

The second reason is to improve the power generation efficiency of the alternator. The rotating shaft 3 to which the rotor of the alternator is fixed is rotationally driven by an engine for driving the automobile via an endless belt and a driven pulley. When the fixed driven pulley is used, when the rotation speed of the drive engine sharply decreases, the rotation speed of the rotor also sharply decreases, and the amount of power generated by the alternator also sharply decreases. On the other hand, if the pulley device with a built-in roller clutch is used as the driven pulley attached to the alternator, even if the rotation speed of the driving engine sharply decreases, the rotation speed of the rotor is reduced by inertial force. Gradually decreases, and power generation continues during that time. As a result, compared with the case where a fixed driven pulley is used, the kinetic energy of the rotating shaft and the rotor can be effectively used to increase the amount of power generated by the alternator. The above description was made for the case where the roller clutch built-in type pulley device is installed on the driven pulley side. However, a roller clutch built-in type pulley device having a similar structure is used for the end portion of the crankshaft on the drive side. Even if it is installed in, the same action and effect can be obtained.

[0012]

In order to improve the durability of the roller clutch built-in type pulley device as described above, it is important to suppress the generation of frictional heat and abrasion powder inside the roller clutch 10. is there. In order to suppress this frictional heat, it is important to reduce the friction between the members that are displaced relative to each other during overrun. On the other hand, when the roller clutch built-in type pulley device is used by incorporating it into the rotation transmitting portion of an engine accessory such as an alternator, the rotating part of the engine accessory rotates at high speed (18000 min in a locked state). ^In addition, in the overrun state based on the fluctuation of the rotational angular velocity of the engine, the relative rotational speed between the inner wheel 11 and the outer wheel 15 is several thousand min ^−1.
Reach the level.

On the other hand, in the case of the conventional structure shown in FIG. 9,
The pair of support bearings 9, 9 and the roller clutch 10 are provided by the inward flange portions 23a, 23b provided at both ends of the outer ring 15.
The rollers 16, 16 are prevented from being displaced in the axial direction. Therefore, in the overrun state, the inner end surface of the retainer of each of the support bearings 9 and 9 and the roller clutch 10 are
In addition to rubbing against the end surface of the clutch holder 17, the outer end surface of the holder of each of the support bearings 9 and 9 and the inner surface of the inward flange portions 23a and 23b may rub against each other. Since each of these end faces rubs against each other on a flat surface, the friction area is widened and not only the generated frictional heat but also the generated abrasion powder is increased.

An increase in frictional heat leads to a rise in temperature inside the pulley device with a built-in roller clutch, which accelerates the deterioration of the grease enclosed therein, leading to a decrease in the durability of the pulley device with a built-in roller clutch. In addition, the generated abrasion powder enters the meshing portion of the roller clutch 10 to cause malfunction and lower durability, and also enters the support bearings 9 and 9 described above to cause vibration and lower durability. . In view of such circumstances, the present invention has been invented to suppress heat generation and abrasion powder generated during overrun.

[0015]

A pulley device with a built-in roller clutch according to the present invention is used for a belt transmission device of an engine accessory, and includes a pulley member and a shaft arranged on the inner diameter side of the pulley member. A member, a roller clutch provided between the pulley member and the shaft member, and a pair of ball bearings provided between the pulley member and the shaft member so as to sandwich the roller clutch from both sides in the axial direction. With.
Of these, the roller clutch locks in one direction of rotation and unlocks in the other direction, and includes a clutch outer diameter portion provided on the inner peripheral portion of the pulley member and an outer peripheral portion of the shaft member. Of the clutch inner diameter portion provided between the outer peripheral surface of the clutch inner diameter portion and the inner peripheral surface of the clutch outer diameter portion, a plurality of rollers, the clutch outer diameter portion and the clutch inner diameter portion A clutch retainer that is provided between the rollers and has a plurality of pockets that hold the above rollers inside. Further, each of the ball bearings is located on the inner peripheral portion of the pulley member, and has a bearing outer diameter portion having an outer ring raceway of circular arc cross section on the inner peripheral surface thereof, and an outer peripheral portion of the shaft member, For a bearing inner diameter portion having an inner ring raceway with an arcuate cross section on its outer peripheral surface, a plurality of balls provided between the inner ring raceway and the outer ring raceway, and a bearing for rotatably holding these balls And a retainer. The movement of the clutch retainer in the axial direction is restricted by the track via the retainer of the ball bearing and the balls.

[0016]

According to the pulley apparatus with a built-in roller clutch of the present invention constructed as described above, the friction between the members which are relatively displaced at the time of overrun is reduced, and the heat generation and abrasion powder generated at the time of overrun are suppressed. I can do things. That is, in the case of the present invention, a ball bearing capable of bearing not only a radial load but also an axial load is used as a bearing for rotatably supporting the shaft member and the pulley member. Therefore, the constituent members of these ball bearings are not displaced in the axial direction with respect to the shaft member and the pulley member, and rotate in synchronization with the constituent members of these ball bearings and the shaft member or the pulley member. There is no friction with the members. Further, there is a possibility that the axial end surface of the clutch retainer and the axial end surface of the bearing retainer may rub against each other during overrun, but the relative rotational speed between these both retainers is relatively large. It is about half of the rotation speed. Therefore, the frictional heat and abrasion powder generated due to the friction between the axial end faces of the both cages can be suppressed to be much smaller than that of the conventional structure. Further, the axial movement of the clutch retainer is restricted by the orbits of the ball bearings via the retainer of the ball bearing and the balls, but the contact state between the balls and the orbit is rolling. Since it is in contact, heat generation at the contact portion is small and wear is unlikely to occur. As a result, the life of the roller clutch portion and the ball bearing portion can be stably and sufficiently ensured.

[0017]

1 shows a first example of an embodiment of the present invention. The roller clutch built-in type pulley device of this example has a sleeve 24 which is a shaft member (rotating shaft member) described in the claims, which can be externally fitted and fixed to the rotating shaft 3 (see FIG. 8) of the alternator 1. Further, a driven pulley 7a, which is a pulley member described in the claims, is arranged around the sleeve 24 concentrically with the sleeve 24. A pair of deep groove type or angular type ball bearings 25, 25 and a roller clutch 10 are provided between the outer peripheral surface of the sleeve 24 and the inner peripheral surface of the driven pulley 7a.

The sleeve 24 is formed into a substantially cylindrical shape as a whole, and is externally fitted and fixed to the end of the rotary shaft 3 of the alternator 1 so as to be rotatable together with the rotary shaft 3. Therefore, in the illustrated example, a threaded hole portion 26 is formed in the intermediate portion of the inner peripheral surface of the sleeve 24, and the threaded hole portion 26 and the male screw portion provided on the outer peripheral surface of the distal end portion of the rotary shaft 3 are screwed together. I am free. Further, a locking hole 27 having a hexagonal cross-section is formed at the tip of the inner peripheral surface of the sleeve 24, and the tip of a tool such as a hexagon wrench can be locked in the locking hole 27. I am trying. Further, the base end portion of the inner peripheral surface of the sleeve 24 is a circular hole portion 28 which can be fitted into the portion of the rotary shaft 3 near the middle of the tip end portion without rattling. Incidentally, as the structure in which the sleeve 24 and the rotary shaft 3 are combined so as not to rotate relative to each other, other structures such as spline engagement, non-circular fitting, and key engagement may be adopted.

On the other hand, the front half of the outer peripheral surface of the driven pulley 7a has a corrugated cross-sectional shape in the width direction so that a part of an endless belt called a poly V belt can be stretched over. Then, the roller clutch 10 is provided at an axially intermediate portion of a space existing between the outer peripheral surface of the sleeve 24 and the inner peripheral surface of the driven pulley 7a, and the roller clutch 10 is also provided at both axially end portions of the space. The ball bearings 25, 25 are respectively arranged at positions sandwiching from both sides in the axial direction.

Of these, the ball bearings 25, 25 support the radial load and the axial load applied to the driven pulley 7a and allow the driven pulley 7a and the sleeve 24 to rotate relative to each other. The ball bearings 25, 25 are
Bearing outer rings 31, 31 having deep groove type or angular type outer ring raceways 30, 30 on their inner peripheral surfaces respectively, and deep groove type or angular type inner ring raceways 32, 3 on their outer peripheral surfaces.
Bearing inner rings 33, 33 having two and the outer ring raceway 3
0, 30 and the inner ring raceways 32, 32, a plurality of balls 34, 34 rotatably provided respectively, and these balls 3
Bearing cages 40 and 40 for holding the bearings 4 and 34. The bearing outer races 31 and 31 are provided on the inner peripheral surfaces of the driven pulley 7a near both ends, and the bearing inner races 33 and 3 are provided.
3 are fitted and fixed to the outer peripheral surfaces of the sleeve 24 near both ends. Further, by providing seal rings 29, 29 between the inner peripheral surfaces of the outer ends of the bearing outer rings 31, 31 and the outer peripheral surfaces of the outer ends of the bearing inner rings 33, 33, respectively, the balls are provided. The bearings 25, 25 and the inner space of the roller clutch 10 are disconnected from the outside.

Further, the roller clutch 10 is driven by the driven pulley 7a only when the driven pulley 7a tends to rotate relative to the sleeve 24 in a predetermined direction.
The rotation force is freely transmitted between the sleeve and the sleeve 24.
In order to configure the roller clutch 10 as described above, the pair of bearing inner rings 33, 3 is formed at the axially intermediate portion of the sleeve 24.
An inner race 35 for a clutch is externally fitted and fixed to the portion between 3 by an interference fit. The inner ring 35 for the clutch is formed into a cylindrical shape as a whole by subjecting a steel plate such as carburized steel to plastic working such as press working, and has a cam surface 13 formed on the outer peripheral surface. That is, on the outer peripheral surface of the clutch inner race 35, as shown in FIG.
By forming 2 and 12 at equal intervals in the circumferential direction, the outer peripheral surface serves as the cam surface 13.

On the other hand, the inner peripheral surface of the clutch outer race 36, which is internally fitted and fixed to the intermediate portion of the inner peripheral surface of the driven pulley 7a by interference fitting, is merely a cylindrical surface. Such a clutch outer ring 36 is also formed into a cylindrical shape by subjecting a steel plate such as carburized steel to plastic working such as press working.

Further, the plurality of rollers 16 constituting the roller clutch 10 together with the clutch inner race 35 and the clutch outer race 36 are fitted onto the clutch inner race 35 so that the clutch inner race 35 cannot rotate. The clutch retainer 37 is supported so that it can be rolled and slightly displaced in the circumferential direction. The clutch holder 37 is made of synthetic resin (for example, synthetic resin such as polyamide 66, polyamide 46, and polyphenylene sulfide mixed with about 20% of glass fiber) and is formed into a cage-shaped cylindrical shape. A pair of rim portions 38, 38 each having an annular shape, and a plurality of pillar portions 21, 21 (see FIG. 10).
(Refer to).

The portions surrounded by the inner side surfaces of the rim portions 38, 38 and the side surfaces of the column portions 39, 39 in the circumferential direction for four turns are respectively rolled by the rollers 16 in the circumferential direction. The pockets 41 and 41 are provided for holding a slight amount of displacement. Then, the respective rim portions 38, 3
As shown in FIG. 10, the protrusions 19 and 19 formed at a plurality of inner peripheral surfaces of the clutch inner ring 35 (1
By engaging with the recesses 12, 12 formed on the outer peripheral surface of 1), the clutch holder 37 is mounted on the clutch inner ring 35 such that relative rotation with respect to the clutch inner ring 35 is impossible.

Further, as shown in FIG. 10, the spring 22 is attached to one side surface in the circumferential direction of the pillar portions 39, 39 constituting the clutch holder 37. The spring 22 provided for each of the pillar portions 39, 39 has the cam surface 13 formed on the outer peripheral surface of the clutch inner ring 35 and the roller outer ring 36 for the roller 16 held in the pockets 41, 41. Among the substantially cylindrical gaps formed between the inner peripheral surface (cylindrical surface) of the intermediate portion, toward the portion where the width in the diametrical direction is narrowed, in the same direction in the circumferential direction of the clutch retainer 37 (FIG. It is elastically pressed to the right of 10 = clockwise).

Further, in the case of the roller clutch built-in type pulley device of the present invention, both axial end faces of the clutch retainer 37 and the bearing retainers 40 of the ball bearings 25, 25,
By engaging with the axial end surface of 40, the axial displacement of the clutch holder 37 is restricted. For this reason, in the case of this example, both end portions 3 in the axial direction of the clutch holder 37 are
7 is extended outward in the axial direction so that the clutch holder 37
The two axial end faces 42, 42 of the bearing retainer 4
It is closely opposed to the axial end faces of 0 and 40.

In the case of the present embodiment, as each of the bearing cages 40, 40, a corrugated press cage formed by bending a metal plate is used. Therefore, the shape in the circumferential direction of the axial end faces of the bearing cages 40, 40 is wavy. The axial end faces of the bearing retainers 40, 40 as described above and the axial end faces 42, 4 of the clutch retainer 37.
Even when they are engaged (contacted) with each other, both of these cages 4
The shape of the clutch holder 37 in the circumferential direction is a straight line having no irregularities so that the relative rotation of the clutches 0 and 37 can be performed smoothly. On the other hand, the shape in the radial direction is not particularly limited. It may be linear or convex arc-shaped.

According to the pulley device with a built-in roller clutch of the present invention constructed as described above, the friction between the members which are displaced relative to each other at the time of overrun is reduced, and the heat generation and abrasion powder generated at the time of this overrun are suppressed. I can do things.
That is, in the case of the present invention, the sleeve 24 and the driven pulley 7 are
As a bearing for rotatably supporting a and a, a ball bearing 25, 2 capable of supporting not only a radial load but also an axial load
I am using 5. Therefore, these ball bearings 25, 25
Bearing outer rings 31, 31, bearing inner rings 33, 33, balls 34, 34, and bearing cages 40, 40.
However, there is no axial displacement with respect to the sleeve 24 and the driven pulley 7a. Therefore, these bearing outer rings 31,
31, bearing inner rings 33, 33, balls 34, 34, bearing cages 40, 40, and the sleeve 24 or the driven pulley 7
A member that rotates in synchronization with a does not rub against each other. Since the contact state inside each of the ball bearings 25, 25 is rolling contact, the friction inside each of the ball bearings 25, 25 is low, and the generated friction heat and abrasion powder are very small.

Also, the clutch retainer 37 during overrun
End face 42 of either of the axial end faces 42, 42 of
And there is a possibility that any one of the bearing retainers 40 will rub against the axial end surface. However, the relative rotational speed between the retainers 37 and 40 is determined by the sleeve 24 and the driven pulley 7a.
It is about half of the relative rotation speed with. Therefore, the frictional heat and abrasion powder generated due to the friction between the axial end faces of both the cages 37 and 40 can be suppressed to be much smaller than that of the conventional structure.

Next, FIG. 2 shows a second embodiment of the present invention.
An example is shown. In the case of this example, the bearing cage 40a
Is a crown-shaped one formed by injection molding a synthetic resin, and the inner end surface of the annular portion 39 of the bearing holder 40a is made to face the end surface 42 of the rim portion 38 of the clutch holder 37. There is. In the case of this example as described above, the shape of the inner end surface of the annular portion 39 of the bearing retainer 40a in the circumferential direction can be made linear. Therefore, the clutch holder 3
The shape in the circumferential direction of the end surface 42 of the rim portion 38 of No. 7 is
It does not necessarily have to be linear (of course, it may be linear). The configuration and operation of the other parts are the same as those of the first embodiment described above.
Since it is similar to the example, illustration and description of equivalent parts will be omitted.

Next, FIG. 3 shows a third embodiment of the present invention.
An example is shown. In the case of this example, the roller clutch 10
A clutch outer ring equivalent portion 43 for forming a is provided integrally with the driven pulley 7a, and a clutch inner ring equivalent portion 44 is provided integrally with the sleeve 24. The configuration and operation of the other parts are the same as in the case of the above-described first example, and thus duplicated description will be omitted.

Next, FIGS. 4 to 7 show fourth to seventh examples of the embodiment of the present invention. First, in the case of the fourth example shown in FIG. 4, the clutch outer ring 36 is fitted in and fixed to the inner peripheral surface axial middle portion of the driven pulley 7a, and the clutch outer ring 36 is formed at the outer peripheral surface axial middle portion of the sleeve 24. The inner ring equivalent portion 44 is integrally formed. Next, in the case of the fifth example shown in FIG. 5, the clutch inner ring 35 is provided at the axially intermediate portion of the outer peripheral surface of the sleeve 24.
Is externally fitted and fixed, and the clutch outer ring equivalent portion 43 is integrally formed at the axially intermediate portion of the inner surface of the driven pulley 7a. Next, in the case of the sixth example shown in FIG. 6, one ball bearing 25
A portion corresponding to the inner ring forming a is integrally formed with the sleeve 24, and a portion corresponding to the outer ring is also integrally formed with the driven pulley 7a. Further, in the case of the seventh example shown in FIG. 7, the clutch outer ring equivalent portion 43 for configuring the roller clutch 10a is integrated with the driven pulley 7a, and the clutch inner ring equivalent portion 44 is integrated with the sleeve 24. In addition to being provided respectively, a portion corresponding to the inner ring forming one ball bearing 25a is formed integrally with the sleeve 24, and a portion corresponding to the outer ring is formed integrally with the driven pulley 7a. The configurations and operations of the other parts of the fourth to seventh examples shown in FIGS. 4 to 7 are the same as those of the first example described above, and therefore, duplicated description will be omitted. When the portions corresponding to the inner ring and the outer ring of any one of the pair of ball bearings are integrated with the sleeve or the driven pulley, which one of the ball bearings is to be integrated Determined in consideration of durability required for ball bearings and ease of assembly. In this case, the side on which the integrated type ball bearing is provided may be reversed from the illustrated example.

[0033]

Since the present invention is configured and operates as described above, it is possible to realize a roller clutch built-in type pulley device having excellent durability by suppressing frictional heat and abrasion powder generated at the time of overrun.

[Brief description of drawings]

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

FIG. 2 is a view showing a second example of the same and corresponds to a portion A in FIG. 1;

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

FIG. 4 is a half sectional view showing the fourth example.

FIG. 5 is a half sectional view showing the fifth example.

FIG. 6 is a half sectional view showing the sixth example.

FIG. 7 is a half sectional view showing the seventh example.

FIG. 8 is a sectional view showing an example of a conventional alternator.

FIG. 9 is a sectional view showing an example of a conventional pulley device with a built-in roller clutch.

10 shows an example of a conventional structure of a roller clutch to be incorporated into a pulley device with a built-in roller clutch, B in FIG.
-The figure corresponding to a B cross section.

[Explanation of symbols]

1 alternator 2 housing 3 rotation axes 4 Rolling bearing 5 rotor 6 commutator 7,7a pulley 8 sleeves 9 Support bearing 10, 10a Roller clutch 11 inner ring 12 recess 13 Cam surface 14 Inner ring track 15 outer ring 16 roller 17 Clutch retainer 18 Cylindrical gap 19 convex 20 pockets 21 Pillar 22 spring 23a, 23b Inward collar part 24 sleeves 25, 25a ball bearing 26 screw holes 27 Lock hole 28 Round hole 29 seal ring 30 outer ring orbit 31 Bearing outer ring 32 Inner ring track 33 Bearing inner ring 34 balls 35 clutch inner ring 36 clutch outer ring 37 Clutch retainer 38 Rim section 39 Annular part 40, 40a Bearing cage 41 pockets 42 Edge 43 Outer ring equivalent part for clutch 44 Inner ring equivalent part for clutch

Claims (2)

[Claims] 1. A belt transmission device for an engine accessory, comprising a pulley member, a shaft member arranged on the inner diameter side of the pulley member, and a roller provided between the pulley member and the shaft member. A clutch and a pair of ball bearings provided between the pulley member and the shaft member so as to sandwich the roller clutch from both sides in the axial direction are provided. A. Which is locked in one direction and unlocked in the other direction, the clutch outer diameter portion provided on the inner peripheral portion of the pulley member, and the clutch inner diameter portion provided on the outer peripheral portion of the shaft member, A roller provided between the outer peripheral surface of the clutch inner diameter portion and the inner peripheral surface of the clutch outer diameter portion, and a roller provided between the clutch outer diameter portion and the clutch inner diameter portion and holding the roller inside. Club with pockets A ball bearing outer diameter portion having an outer ring raceway on the inner peripheral surface of the pulley member, and the shaft member. A bearing inner diameter portion having an inner ring raceway on its outer circumferential surface, a ball provided between the inner ring raceway and the outer ring raceway, and a bearing retainer for rotatably holding the ball. C. A pulley device with a built-in roller clutch, wherein the movement of the clutch retainer in the axial direction is restricted by the raceway via the retainer of the ball bearing and the balls. 2. The shape in the circumferential direction of at least one of the axial end surfaces of the clutch retainer and the bearing retainer that are opposed to each other is a straight line having no irregularities, A pulley device with a built-in roller clutch according to claim 1.