JP2001099272A - One-way clutch built-in type pulley device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide structure to sufficiently ensure durability. SOLUTION: A holder 43 for a clutch comprising a one-way clutch 10a is rotated together with a sleeve 8a. Displacement in the axial direction of the holder 43 for a clutch based on a driven pulley 7b is regulated in a way that the inside surfaces of a pair of flange parts 39a and 39b situated at the two ends in the axial direction of an outer ring 38 for a one-way clutch securely fitted in internally of the driven pulley 7b and the two end faces in the axial direction of the holder 43 for a clutch are situated facing each other. simultaneously, the size of a gap in the axial direction between the holder 43 for a clutch and the two flange parts 39a and 39b is set to 0.2 mm or more.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pulley device with a built-in one-way clutch. The alternator is used to drive the alternator by passing an endless belt between them.

[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. 8 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. At one end (right end in FIG. 8) of the rotary shaft 3, a portion protruding outside the housing 2 is provided with a driven pulley 7.
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 one-way clutch built-in pulley devices that allow the relative rotation between a driven pulley and a rotating shaft have been proposed and used in some. For example, JP
JP-A-6-101353, JP-A-7-317807, JP-A-8-226462, JP-A-9-229097, JP-B-7-72585, and French Patent Publication FR2726059A1 have the above-described functions. A one-way clutch built-in pulley device is described.
In some cases, such a pulley device with a built-in one-way clutch is actually used.

[0004] FIG. 9 is a diagram showing an example of Japanese Patent Application Laid-Open No. Hei 8-22646.
2 shows a one-way clutch-incorporated pulley device described in Japanese Patent Publication No. 2 (JP-A) No. 2 (1994). This one-way clutch built-in pulley device has a sleeve 8 which can be fitted and fixed to the rotating shaft 3 of the alternator 1 (FIG. 8). A driven pulley 7 a is arranged around the sleeve 8 concentrically with the sleeve 8. A pair of support bearings 9 and 9 and a one-way clutch 10 are provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a. The support bearings 9 support the radial load applied to the driven pulley 7a, and allow the relative rotation between the sleeve 8 and the driven pulley 7a. The one-way clutch 10
Makes it possible to freely transmit the rotational force 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.

[0005] The one-way clutch 10 is formed, and an outer peripheral surface of an intermediate portion of an inner ring 11 which is externally fitted and fixed to the sleeve 8 is provided.
A plurality of concave portions 12, 12 called ramp portions are formed at equal intervals in the circumferential direction, and the outer peripheral surface of the intermediate portion is cam surface 1
It is set to 3. The outer peripheral surfaces of both ends of the inner ring 11 are inner ring raceways 14 for the support bearings 9. On the other hand, the inner peripheral surface of the outer race 15 which is fitted and fixed to the driven pulley 7a constituting the one-way clutch 10 is a simple cylindrical surface over substantially the entire length. or,
The plurality of rollers 16, 16 constituting the one-way clutch 10 together with the inner ring 11 and the outer ring 15 are provided on a clutch retainer 17 rotating together with the inner ring 11 so as to freely roll and slightly displace in the circumferential direction. I support it. A spring is provided between the column provided on the clutch retainer 17 and each of the rollers 16. These springs reduce the width of the rollers 16, 16 in the diametrical direction among the dimensions of the cylindrical gap formed between the outer peripheral surface of the cam surface 13 and the inner peripheral surface of the outer ring 15. It is elastically pressed toward the part. In addition, flanges 18, 18 each having an inward flange shape are provided at both axial ends of the outer ring 15. The axial inner side surfaces of these flanges 18, 18 are in close proximity to or abut one axial end surfaces of the retainers 19, 19 constituting the support bearings 9, 9.

The reason for using the pulley device with a built-in one-way clutch as described above is as follows. For example, when the running 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 driven to rotate by the endless belt via the driven pulley 7a,
And a rotor 5 and a commutator 6 fixed to the rotating shaft 3.
It does not fluctuate so rapidly based on the inertial mass such as (FIG. 8). Therefore, when the driven pulley 7a is simply fixed to the rotating shaft 3, the rotating speed of the rotating shaft 3 is directly reduced when the running speed of the belt is reduced, and the power generation efficiency of the alternator 1 is reduced. At the same time, the endless belt and the driven pulley 7a tend to rub in both directions with 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 7a, so that slipping easily occurs between the endless belt and the driven pulley 7a, or the life of the endless belt is reduced. It may be shortened.

In addition, the above-described reduction in the power generation efficiency of the alternator and the reduction in the life of the endless belt due to friction between the outer peripheral surface of the driven pulley 7a and the inner peripheral surface of the endless belt are caused by repeated acceleration and deceleration during traveling. Also occurs. That is, the driving force is transmitted from the endless belt side to the driven pulley 7a side during acceleration, whereas the braking force from the endless belt is applied to the driven pulley 7a that continues to rotate based on inertia as described above during deceleration. Works. 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 on the inner peripheral surface of the endless belt in a reverse direction. It causes a decline. In particular, in the case of a vehicle equipped with an exhaust brake such as a truck, the deceleration of the decrease in rotation of the crankshaft when the accelerator is off is remarkable, and the frictional force applied to the inner peripheral surface of the endless belt based on the braking force As a result, the power generation efficiency and the life are significantly reduced.

Therefore, the pulley device with a built-in one-way clutch is used as the driven pulley 7a as described above.
Accordingly, when the traveling speed of the endless belt is constant or increasing, the rollers 16, 16 constituting the one-way clutch 10 are positioned between the outer peripheral surface of the inner race 11 and the inner peripheral surface of the outer race 15. Of the dimensions of the cylindrical gap formed therebetween, bites into a portion where the width in the diametrical direction is reduced (locked), so that the rotational force can be freely transmitted from the driven pulley 7a to the rotary shaft 3. I do. Conversely, when the running speed of the endless belt tends to decrease, each of the rollers 16, 16 moves to a portion of the cylindrical gap having a larger width, and each of the rollers 16, 16 moves to the corresponding portion. , So that the driven pulley 7a and the rotating shaft 3 can freely rotate relative to each other. That is, when the running speed of the endless belt tends to decrease, the rotational angular speed of the driven pulley 7a 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 7a is reduced. To prevent strong rubbing.
In this way, the power generation efficiency of the alternator is ensured, the direction of the stress acting on the rubbed portion between the driven pulley 7a and the endless belt is made constant, and slippage occurs between the endless belt and the driven pulley 7a. Or the life of the endless belt is prevented from being shortened.

Japanese Patent Application Laid-Open No. 9-229097 discloses that
The axial length of the outer ring fitted and fixed to the driven pulley is shorter than that of the structure described in Japanese Patent Application Laid-Open No. 8-226462, and each of the outer rings is provided at both ends in the axial direction of the outer ring. A structure is described in which a pair of inward flange-shaped flanges has inner surfaces in the axial direction opposed to both end surfaces in the axial direction of a clutch retainer constituting a one-way clutch. According to such a structure, it is possible to prevent the axial position of the clutch retainer from being largely shifted.

[0010]

SUMMARY OF THE INVENTION The above-mentioned Japanese Patent Application Laid-Open No. 9-22 / 1990
No. 9097, the axially inner surfaces of a pair of flanges provided on an outer ring fixedly fitted to a driven pulley are opposed to the axially opposite end surfaces of a clutch retainer. In the case of a pulley device with a built-in one-way clutch that regulates the displacement of the retainer in the axial direction, the clutch retainer is displaced in the axial direction during overrun when the driven pulley and the sleeve rotate relative to each other ( (Wobble) while rotating relative to the outer ring. Therefore, in such a case, at the time of overrun, the axial end surfaces of the clutch retainer and the axial inner side surfaces of the pair of flange portions may rub against each other. In particular, if the axial gap between the axial end surfaces and the axial inner surface is too small, the thrust load applied between the clutch retainer and the flange tends to increase. Then, the PV value (the product of the contact pressure and the sliding speed), which represents the degree of the sliding friction and greatly affects the calorific value, increases. Therefore, when the axial gap is not appropriate, the heat generated due to the sliding contact as described above increases, and based on this heat, the clutch retainer is thermally deformed or the one-way clutch becomes The grease existing for lubrication may be thermally degraded. Such thermal deformation of the clutch retainer and thermal degradation of the grease are undesirable because they cause the durability of the pulley device with a built-in one-way clutch to be impaired. In particular, when a one-way clutch built-in type pulley device is used for an alternator, the relative rotation speed between the sleeve and the driven pulley may reach up to several thousand min ⁻¹ (rpm). The adverse effects due to the rubbing are remarkable. The present invention has been made in consideration of the above-described circumstances, and reduces the degree of friction between a clutch retainer and another member that is different from the clutch retainer during overrun of a one-way clutch. The invention has been made in order to prevent the adverse effects due to the rubbing.

[0011]

A pulley device with a built-in one-way clutch according to the present invention has a sleeve which can be externally fitted and fixed to a rotating shaft, like a pulley device with a built-in one-way clutch. A driven pulley disposed concentrically with the sleeve around the sleeve, and provided between a part of the outer peripheral surface of the sleeve and a part of the inner peripheral surface of the driven pulley, and the driven pulley is moved in a predetermined direction with respect to the sleeve. A one-way clutch that enables the transmission of rotational force between these driven pulleys and the sleeve only when there is a tendency to rotate relatively;
Between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley,
The one-way clutch is provided at a position deviated in the axial direction, and includes a support bearing that supports the radial load applied to the driven pulley and allows relative rotation between the sleeve and the driven pulley.

In particular, in the pulley device with a built-in one-way clutch of the present invention, the clutch retainer constituting the one-way clutch rotates together with one of the sleeve and the driven pulley. The clutch retainer has both ends in the axial direction opposed to a pair of opposite side surfaces provided on the other member of the sleeve and the driven pulley or a member that rotates together with the other member. The axial length between the pair of side surfaces is set to be 0.2 mm or more larger than the axial length of the clutch retainer.

[0013]

According to the pulley device with a built-in one-way clutch of the present invention constructed as described above, the clutch retainer is displaced (wobble) in the axial direction during the overrun in which the sleeve and the driven pulley relatively rotate. Even when relatively rotated with respect to the other member of the sleeve and the driven pulley, both ends in the axial direction of the clutch retainer are provided on the other member or the member that rotates together with the other member. It is possible to prevent the pair of side surfaces facing each other from strongly rubbing each other. When the heat generated due to such friction increases, the clutch retainer may be thermally deformed, or the grease existing for lubrication in the one-way clutch may be thermally deteriorated. In such a case, such inconvenience can be prevented, and the durability of the pulley device with a built-in one-way clutch can be sufficiently ensured.

[0014]

1 to 3 show a first embodiment of the present invention. The one-way clutch built-in pulley device for the alternator of the present example is formed in a cylindrical shape as a whole,
The alternator includes a sleeve 8a externally fitted and fixed to the end of the rotating shaft 3 (see FIGS. 8 and 9) of the alternator, and a driven pulley 7b disposed around the sleeve 8a and concentrically with the sleeve 8a. The sleeve 8a is rotatable with the rotation shaft 3. For this reason, in the illustrated example, a female screw portion 23 is formed on the inner peripheral surface of the intermediate portion of the sleeve 8a, and the female screw portion 23 and a male screw portion (not shown) formed on the outer peripheral surface of the end of the rotary shaft 3 are screwed. It is free to fit. The structure for preventing the relative rotation between the rotary shaft 3 and the sleeve 8a may be a spline, a fitting between non-cylindrical surfaces, a key engagement, or the like instead of the screw. Further, in order to facilitate the screwing operation between the female screw portion 23 and the male screw portion, a tip of a tool such as a hexagon wrench is engaged with the inner peripheral surface of one end (the left end in FIG. 1) of the sleeve 8a. A hexagonal hole 24 that can be stopped is formed.

The driven pulley 7b provided around the sleeve 8a has a pair of support bearings 25, 25 and a one-way clutch 10a described below mounted inside the driven pulley 7b. or,
The outer peripheral surface of one half (the left half in FIG. 1) of the driven pulley 7b has a cross-sectional shape extending in the width direction and has a waveform, so that a part of an endless belt called a poly-V belt can be freely passed over.

In the case of this embodiment, a pair of support bearings 25, each of which is a deep groove type ball bearing, is provided between the outer peripheral surface of the sleeve 8a and the inner peripheral surface of the driven pulley 7b.
25, and one one-way clutch 10a which is a roller clutch. Each of these support bearings 2
Reference numerals 5 and 25 denote inner rings 27 each having a deep groove type inner raceway 26 on the outer peripheral surface, outer races 29 each having a deep groove type outer raceway 28 on the inner peripheral surface, and between the inner raceway 26 and the outer raceway 28, respectively. Rolling elements (balls) provided so that they can roll freely
30 and 30. Then, the outer ring 29 is attached to the inner peripheral surface of the driven pulley 7b at a portion near both ends of the driven pulley 7b.
Are fitted and fixed to the step portions 31 formed on the outer peripheral surfaces of both ends of the sleeve 8a over the entire circumference, respectively, by interference fitting. In this state, the inner rings 27 are
The one edge in the axial direction is connected to the step portions 31 and 31 and the sleeve 8.
The support bearings 25, 25 are prevented from slipping in the axial direction with respect to the sleeve 8 a by abutting the step surfaces 32, 32 between the outer peripheral surface of the main body portion a of FIG.

Each of the rolling elements 30, 30 has a plurality of pockets 3 provided in a retainer 33 formed in an annular shape as a whole.
Rolls 4 and 34 are provided so as to freely roll. Seal rings 35 are provided between the outer peripheral surfaces of both ends of each inner ring 27 and the inner peripheral surfaces of both ends of each outer ring 29.
Each of these seal rings 35 is composed of a metal core 20 in which a metal plate such as a steel plate is formed in an annular shape, and an elastic material 21 such as an elastomer such as rubber. The outer peripheral edge of each seal ring 35 is fixed to the inner peripheral surface of both ends of each outer ring 29, and the inner peripheral edge of the elastic member 21 is brought into sliding contact with the outer peripheral surface of both ends of each inner ring 27. . And
These seal rings 35 prevent foreign substances from entering the space where the plurality of rolling elements 30 exist from the outside, and grease existing in the support bearings 25 leaks to the outside. Is prevented.

Further, in order to constitute the one-way clutch 10a, an inner ring 36 for one-way clutch is externally fixed to the outer peripheral surface of the sleeve 8a in the axially intermediate portion by interference fit. The one-way clutch inner ring 36 is formed entirely of a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415 into a cylindrical shape, and the outer peripheral surface is a cam surface 37.

On the other hand, an outer ring 38 for a one-way clutch is fixedly fitted on the inner peripheral surface of the intermediate portion of the driven pulley 7b by interference fitting. The outer ring 38 for a one-way clutch, which is also formed in a cylindrical shape as a whole by pressing a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415, is provided with inward flanges at both ends in the axial direction. Formed flange portions 39a and 39b are formed. In addition, these both collar parts 3
9a and 39b, one (left side of FIGS. 1 and 3) flange 3
9a has the same thickness dimension as the main body of the outer ring 38 for the one-way clutch, because it is formed before being combined with other constituent members. On the other hand, the other side (right side in FIGS. 1 and 3) of the flange portion 39b is formed to be thin after being combined with other components. Each such flange 39
a, 39b are provided on the respective support bearings 2 in the axial direction.
The inner rings of the outer races 29, 29 constituting the fifth and fifth gears 25, respectively, are brought into close contact with each other or with small gaps therebetween.

At a plurality of locations on the outer peripheral surface of the one-way clutch inner ring 36, recesses 40, 40, called ramps, whose depth increases as going in a predetermined direction with respect to the circumferential direction.
Are formed at equal intervals in the axial direction and in the circumferential direction of the one-way clutch inner ring 36, and the outer peripheral surface of the one-way clutch inner ring 36 is the cam surface 37. A cylindrical gap 41 is formed between the outer peripheral surface of the one-way clutch inner ring 36 and the inner peripheral surface of the one-way clutch outer ring 38. The width dimension of the outer ring 38 for the directional clutch and the inner ring 36 for the one-way clutch in the diametrical direction is determined by the number of the rollers 42, 42 provided in the cylindrical gap 41 in the portion corresponding to the deepest portion of each of the recesses 40, 40. The outer diameter of each roller 42 is greater than the outer diameter of the roller 42, and the portion outside the recesses 40 is smaller than the outer diameter of each of the rollers 42.

The one-way clutch 10a has a cage-like cylindrical shape formed of a synthetic resin between the inner peripheral surface of the one-way clutch outer race 38 and the outer peripheral surface of the one-way clutch inner race 36. It comprises a retainer 43 and a plurality of the rollers 42, 42 and springs 44, 44, respectively. The clutch retainer 43 includes a pair of rims 45, 45 each having an annular shape, and a plurality of pillars 46, 46 connecting the two rims 45, 45 to each other. Then, a portion surrounded by the inner side surface of each of the rim portions 45, 45 and the side surface of each of the pillar portions 46, 46 on four sides is
A plurality of pockets 47 are provided for holding each roller 42 so as to be able to roll and slightly displace in the circumferential direction. Then, the convex portions 48, 48 formed at a plurality of locations on the inner peripheral surface of the rim portions 45, 45 are engaged with the concave portions 40, 40 formed on the outer peripheral surface of the one-way clutch inner race 36, whereby The clutch retainer 43 is attached to the one-way clutch inner race 36, and the one-way clutch inner race 36
Is mounted so that relative rotation with respect to is impossible. The springs 44 are provided between the pillars 46, 46 constituting the clutch retainer 43 as described above and the rollers 42, and the rollers 42 are the same in the circumferential direction. It is elastically pressed in the direction (left direction in FIG. 2).

In particular, in the case of the present invention, both axial end faces of the clutch retainer 43 are axially aligned with both flange portions 39a and 39b provided at both axial end portions of the one-way clutch outer ring 38. By opposing the side surfaces, the displacement of the clutch retainer 43 in the axial direction with respect to the driven pulley 7b is restricted. Simultaneously, in the present case, as compared with the axial length L ₄₃ of the clutch retainer 43, the both flange portions 39a, the axial length L ₃₉ between the inner surfaces of the 39 b, 0 .2mm or more. For example, in the case of this example, the axial length L ₄₃ of the clutch retainer 43, the both flange portions 39a, than the axial length L ₃₉ between the inner surfaces of the 39 b, about 0. 4mm shorter. By restricting in this way, as shown in FIG. 3, one axial end face of the clutch retainer 43 is
a, 39b, in the state where it abuts against the inner surface of one flange 39a, the other end in the axial direction of the clutch retainer 43 and the other flange 3 of the two flanges 39a, 39b.
About 0.4 mm in axial thickness between the inner surface of
Is formed.

In the case of this embodiment, a conical convex chamfer 4 is formed on the outer peripheral surface of the pair of rims 45, 45 provided at both ends in the axial direction of the clutch retainer 43 in the axial direction.
9 and 49 are formed respectively. In the case of the present example, by forming the chamfers 49, 49 in this manner, the axial inner surfaces of the flanges 39a, 39b provided on the outer ring 38 for the one-way clutch and the axial direction of the retainer 43 for the clutch are formed. Before the end faces come into contact with each other, a continuous portion between the axially inner side surfaces of the flange portions 39a and 39b and the inner peripheral surface of the main body portion of the one-way clutch outer ring 38 and the clutch retainer 43 interfere with each other. Is preventing things.

In the pulley apparatus with a built-in one-way clutch of the present invention constructed as described above, the one-way clutch 10a has a driven pulley 7b in which the outer ring 38 for one-way clutch is fixed and a rotation in which the sleeve 8a is fixed. Only the rotational force in a predetermined direction is transmitted to and from the shaft 3. For example, in FIG. 2, assuming that the one-way clutch inner ring 36 is fixed and only the one-way clutch outer ring 38 rotates, when the one-way clutch outer ring 38 rotates clockwise in FIG. As shown by the solid line in FIG. 2, each of the concave portions 40, 40 is opposed to the elasticity of each of the springs 44, 44 based on the force that each roller 42 receives from the inner peripheral surface of the one-way clutch outer ring 38. Tends to be displaced toward the deeper side. Then, each of the rollers 42 becomes rotatable in the cylindrical gap 41, and the transmission of rotational force between the one-way clutch outer ring 38 and the one-way clutch inner ring 36 is stopped. ,
This is a so-called overrun state. Conversely, when the one-way clutch outer ring 38 rotates counterclockwise in FIG.
Based on the force received by the rollers 42 from the inner peripheral surface of the outer ring 38 for the one-way clutch and the resilience of the springs 44, 44, the recesses 40, 40 as shown by chain lines in FIG.
Wedges into the shallow side. Then, the one-way clutch outer ring 38 and the one-way clutch inner ring 36 are integrally connected, and the one-way clutch outer ring 38 is connected.
A so-called locked state in which torque can be freely transmitted between the motor and the one-way clutch inner ring 36.

By repeating these operations, the endless belt stretched over the driven pulley 7b and the driven pulley 7b
With the direction of the stress acting on the rubbing part with b constant,
It is possible to prevent the occurrence of slippage between the endless belt and the driven pulley 7b or to reduce the life of the endless belt. Further, when the rotation speed of the engine decreases and the running speed of the endless belt tends to decrease, the relative rotation between the sleeve 8a and the driven pulley 7b becomes free (overrun state). Regardless of the variation, the rotating shaft 3 of the alternator is rotated at a certain high speed based on the rotating inertia force of the rotating shaft 3 itself and the rotor 5 and the commutator 6 (FIG. 8) fixed to the rotating shaft 3. The rotation can be continued, and the power generation efficiency of the alternator can be improved.

In particular, according to the pulley device with a built-in one-way clutch of the present invention, when the sleeve 8a and the driven pulley 7b rotate relative to each other, the clutch retainer 43 is displaced in the axial direction while the driven pulley 7b , Both ends in the axial direction of the clutch retainer 43,
Provided at both axial ends of the one-way clutch outer ring 38,
It is possible to prevent the inner surfaces of the opposite flange portions 39a, 39b from strongly rubbing against each other. When the heat generated due to such friction increases, the clutch retainer 43
May be thermally deformed, or the grease present for lubrication in the one-way clutch 10a may be thermally degraded.
In the case of the present example, the clutch retainer 43 and the both flanges 3
Since the axial gap D between the shafts 9a and 39b is increased to about 0.4 mm, the above-described inconvenience can be prevented, and the durability of the one-way clutch built-in pulley device can be sufficiently ensured.

In this embodiment, the axial dimension of the gap D is about 0.4 mm, but the axial dimension of the gap D is
As a large value of about 5 mm, the both flanges 39a, 39b
The space existing between the inner side surface of the shaft and both end surfaces in the axial direction of the clutch retainer 43 can be used as a grease reservoir. According to this configuration, the grease accumulated in the space is closed at both axial ends of the space by the flange portions 39a and 39b, so that centrifugal force acts on the grease when the pulley device is used. Also, there is no leakage to the outside from between the two flanges 39a and 39b. Therefore, the grease can be evenly spread on the inner peripheral surface of the one-way clutch outer ring 38. Accordingly, the rolling surfaces of the rollers 42, 42 constituting the one-way clutch 10a and the outer ring 38 for the one-way clutch, which are parts that require grease during overrun, are used.
A sufficient amount of grease can be supplied to a portion between the inner peripheral surface and the inner peripheral surface, and the intervening portion can be sufficiently lubricated.

It should be noted that even if the axial dimension of the gap D is set to a large value of about 5 mm as described above, the clutch retainer 4
The gap between the projections 48, 48 provided on the inner peripheral surface of the inner ring 3 and the recesses 40, 40 provided on the outer peripheral surface of the one-way clutch inner ring 36 is reduced, or When the clutch retainer 43 has a slight interference, it is possible to prevent the clutch retainer 43 from being largely displaced in the axial direction, thereby preventing the backlash in the one-way clutch 10a from becoming remarkable. Further, as described above, by setting the axial dimension of the gap D to a large value of about 5 mm, the axial dimension of the gap D can be adjusted to each of the support bearings 25 and 2.
5 and the respective support bearings 25, 2
If the value is larger than the sum of the elastic deformation based on the axial load at 5 and the pulley device, the sleeve 8
a and the driven pulley 7b are relatively displaced in the axial direction,
Heat can be reliably prevented from being generated due to contact between the axial both end surfaces of the clutch retainer 43 and the inner surfaces of the flange portions 39a and 39b provided on the one-way clutch outer ring 38.

Next, an experiment conducted by the inventor of the present invention to confirm the effect of the present invention will be described. In the experiment, in the one-way clutch built-in pulley device having the structure of the present example, the axial dimension of the gap D between the clutch retainer 43 and the flanges 39a and 39b provided on the one-way clutch outer ring 38. Are prepared in various ways, and the driven pulley 7b is set to 11500
After rotating at a rotation speed of n ^-1 (rpm) for 26 seconds, the driven pulley 7b is rotated by 4 to realize an overrun state.
The process of stopping for seconds was repeated. Then, after such a state in which the locked state and the overrun state were alternately repeated was continued for 100 hours, it was confirmed whether or not the clutch retainer 43 had been thermally deformed. In the pulley apparatus with a built-in one-way clutch, the radial gap between the support bearings 25 is 0.005 to 0.030.
mm range. The results of the experiments performed in this way
It is shown in Table 1.

[0030]

[Table 1]

In Table 1, ○ indicates that thermal deformation did not occur in the clutch retainer 43, and X indicates that thermal deformation occurred in the clutch retainer 43, respectively. As can be seen from the experimental results shown in Table 1, when the axial dimension of the gap D between the clutch retainer 43 and the flanges 39a and 39b is less than 0.20 mm, Although thermal deformation occurs in the retainer 43, when the axial dimension of the gap D is 0.20 mm or more, thermal deformation of the clutch retainer 43 can be prevented. As can be seen from the experimental results, in the case of the present invention,
The clutch retainer 43 and the both flanges 39a, 39b
This is effective in preventing heat generation due to rubbing. Therefore, according to the present invention, thermal deformation of the clutch retainer 43 is prevented, and thermal degradation of grease existing for lubrication in the one-way clutch 10a is reduced.
As a result, the durability of the pulley device can be sufficiently ensured.

Next, FIGS. 4 and 5 show a second example of the embodiment of the present invention. In the case of the present example, unlike the case of the first example described above, the one-way clutch outer ring 38a constituting the one-way clutch 10a is replaced by a simple cylinder without the flange portions 39a and 39b (see FIGS. 1 and 3). It is formed in a shape. This one-way clutch outer ring 38a is a SCM415
The plate material is press-formed to form a cylindrical shape, and then the surface is hardened by carbonitriding and quenching. And
Both ends of the one-way clutch outer ring 38a in the axial direction constitute respective support bearings 25, 25, and each outer ring 29 fixed to the inner peripheral surface of the driven pulley 7b at a position near both ends in the axial direction.
29 is in contact with or close to the inner end face.

In the case of this embodiment, each of these outer rings 29,
29, seal rings 35a, 3 fixed to the inner peripheral surface of the inner end.
The both ends in the axial direction of the clutch retainer 43 constituting the one-way clutch 10a are opposed to the inner side surface of the one-way clutch 5a, and the displacement of the clutch retainer 43 in the axial direction with respect to the driven pulley 7b is regulated. . That is, in the case of this example, the seal rings 35a, 35a fixed to the inner peripheral surfaces of both ends of the outer races 29, 29 are provided on both sides of each of the support bearings 25, 25 with a metal plate such as a steel plate formed in an annular shape. The side surface of the gold 20 is exposed. Of the seal rings 35a, 35a fixed to the inner peripheral surfaces of both ends of the outer races 29, 29, the clutch holding mechanism is mounted on the inner surface of the cored bar 20 constituting the seal ring 35a fixed to the inner peripheral surface of the inner end. Table 43
Are opposed to each other in the axial direction. And this gives
The displacement of the clutch retainer 43 in the axial direction with respect to the driven pulley 7b is restricted. At the same time, in the case of the present embodiment, the core metal constituting the pair of seal rings 35a, 35a for making the axial length of the clutch retainer 43 face both axial end surfaces of the clutch retainer 43. The length in the axial direction between the inner surfaces of 20, 20 is shorter by about 0.4 to 0.6 mm. Accordingly, in a state in which one axial end face of the clutch retainer 43 is abutted against the inner side surface of the cored bar 20 of the seal ring 35a facing the one axial end face, the axial direction of the clutch retainer 43 is A gap having a thickness in the axial direction of about 0.4 to 0.6 mm is formed between the other end surface and the inner surface of the cored bar 20 of the seal ring 35a facing the other end surface in the axial direction. You.

In this embodiment, as in the case of the above-described first embodiment, both ends of the clutch retainer 43 in the axial direction and the inner surface of the core metal 20 of the seal ring 35a are in use during use. The strong rubbing prevents the clutch retainer 43 from being thermally deformed and the grease present in the one-way clutch 10a from being thermally degraded. Can be secured. Note that the displacement of the clutch retainer 43 in the axial direction is caused by the fact that the metal cores 20 and 20 forming the pair of seal rings 35a and 35a opposed to both axial end surfaces of the clutch retainer 43.
In general, the friction coefficient between the synthetic resin clutch retainer 43 and the metal core 20 is determined by the friction coefficient between the clutch retainer 43 and the elastic material 21. It is because it becomes smaller. Therefore,
In the case of this example, even if the clutch retainer 43 and the pair of seal rings 35a, 35a make sliding contact during use, heat generation due to this sliding contact can be suppressed to a small extent. For other configurations and actions,
Since this is the same as the case of the first example described above, the duplicate description will be omitted.

FIG. 6 shows a third embodiment of the present invention.
An example is shown. In the case of this example, the one-way clutch 10
The overall length of the one-way clutch outer ring 38b that constitutes a is increased. The one-way clutch outer ring 38b
Outer rings 29, 29 forming a pair of support bearings 25, 25 are fixedly fitted to the inner peripheral surface of the inner peripheral surface near both ends in the axial direction by interference fitting. The one-way clutch outer ring 38b is formed into a cylindrical shape from a plate material made of bearing steel such as SUJ2 and then hardened to increase its hardness. And this one-way clutch outer ring 3
The portion near the outer diameter of 8b is molded on the inner diameter side of the driven pulley 7b made of synthetic resin. Further, the outer peripheral surface of the one-way clutch outer ring 38b was previously subjected to knurling to form irregularities such as serrations, and a part of the one-way clutch outer ring 38b was molded on the driven pulley 7b. In this state, the one-way clutch outer ring 38b
And no creep occurs between the driven pulley 7b and the driven pulley 7b. The driven pulley 7b is formed by injection molding a synthetic resin such as a polyamide resin. By mixing glass fibers into the synthetic resin at a volume of about 25%,
Enough strength is secured.

In the case of the present embodiment, the portions of the clutch retainer 43 constituting the one-way clutch 10a near the outer diameters at both axial end surfaces are fitted inside the portions near the both ends of the one-way clutch outer ring 38b. By opposing the inner ends of the fixed outer rings 29, 29 near the inner diameter, the displacement of the clutch retainer 43 in the axial direction with respect to the driven pulley 7b is restricted. At the same time, in the case of the present example, the axial length of the clutch retainer 43 is set to be about 1.5 to 2.5 mm larger than the axial length between the inner end faces of the outer rings 29, 29. Shortening. Therefore, one end face in the axial direction of the clutch retainer 43 is connected to the two outer races 2.
9 and 29, in the state where it abuts against the inner end face of one outer ring 29, the other end face in the axial direction of the clutch retainer 43 and the inner end face of the other outer ring 29 of the two outer rings 29 and 29. Between 1.5 and 2.5 mm in axial thickness
Is formed.

In the case of this embodiment as well, the clutch retainer 43 is thermally deformed,
The grease existing in the one-way clutch 10a is prevented from being thermally degraded, and the durability of the pulley device with a built-in one-way clutch can be sufficiently ensured. Other configurations and operations are the same as those in the first example described above, and therefore, duplicate description will be omitted.

Next, FIG. 7 shows a fourth embodiment of the present invention.
An example is shown. In the case of this example, the driven pulley 7b is made of steel. A one-way clutch outer ring 38c having the entire length substantially equal to the entire length of the driven pulley 7b is internally fixed to the inner peripheral surface of the driven pulley 7b by interference fitting. As in the case of the above-described third example, this one-way clutch outer ring 38c is also formed in a cylindrical shape from a plate material made of bearing steel such as SUJ2 and then hardened to increase its hardness. is there. In the case of the present example, a small-diameter stepped portion 50 having an inner diameter smaller than that of the portion near both ends is formed on the inner peripheral surface of the intermediate portion of the one-way clutch outer ring 38c. Each of the support bearings 25 is formed on a stepped surface 51, which is a portion between the inner peripheral surface of the small-diameter step portion 50 and the inner peripheral surface near both ends of the one-way clutch outer ring 38c. The outer-diameter portions of the inner end surfaces of the outer rings 29, 29 are abutted, respectively. In this way, the outer rings 29 are prevented from shifting in the axial direction with respect to the one-way clutch outer ring 38c. In the case of this example, the seal ring 35
Are provided only at the outer ends of the support bearings 25, 25, and each of the support bearings 25, 25 has a so-called one-sided seal structure.

In this embodiment, as in the case of the above-described third embodiment, the outer-diameter portions of both ends in the axial direction of the clutch retainer 43 constituting the one-way clutch 10a are connected to the one-way clutch. The inner rings of the outer rings 29, 29, which are internally fitted and fixed to both ends of the outer ring 38c, are closer to the inner diameter.
By opposing each other, displacement of the clutch retainer 43 in the axial direction with respect to the driven pulley 7b is restricted. In the case of this example, the clutch retainer 4 is used.
The axial length of No. 3 is shorter by about 2.0 to 3.0 mm than the axial length between the inner end surfaces of the outer rings 29, 29. For other configurations and operations, see the third embodiment described above.
This is the same as in the example.

[0040]

The pulley apparatus with a built-in one-way clutch according to the present invention is constructed and operates as described above, so that sufficient durability can be ensured.

[Brief description of the drawings]

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

FIG. 2 is an enlarged sectional view taken along the line AA of FIG.

FIG. 3 is an enlarged view of a part B of FIG.

FIG. 4 is a sectional view showing a second example of the embodiment of the present invention.

FIG. 5 is an enlarged view of a portion C in FIG. 4;

FIG. 6 is a sectional view showing a third example of the embodiment of the present invention.

FIG. 7 is a sectional view showing the fourth example.

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

FIG. 9 is a cross-sectional view showing an example of a conventionally known pulley device with a built-in one-way clutch for an alternator.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Alternator 2 Housing 3 Rotating shaft 4 Rolling bearing 5 Rotor 6 Commutator 7, 7a, 7b Followed pulley 8, 8a Sleeve 9 Support bearing 10, 10a One-way clutch 11 Inner ring 12 Depression 13 Cam surface 14 Inner ring raceway 15 Outer ring 16 Roller 17 Clutch retainer 18 Flange part 19 Retainer 20 Core metal 21 Elastic material 23 Male screw part 24 Hexagon hole part 25 Support bearing 26 Inner ring raceway 27 Inner ring 28 Outer ring raceway 29 Outer ring 30 Rolling element 31 Step part 32 Step surface 33 Retainer 34 Pocket 35, 35a Seal ring 36 One-way clutch inner ring 37 Cam surface 38, 38a, 38b, 38c One-way clutch outer ring 39a, 39b Flange part 40 Concave part 41 Cylindrical gap 42 Roller 43 Clutch retainer 44 Spring 45 Rim part 46 Column 47 Pocket 48 Convex 49 chamfer 50 cylindrical portion 51 stepped surface

Claims (1)

[Claims] 1. A sleeve which can be externally fitted and fixed to a rotating shaft, a driven pulley disposed around the sleeve and concentric with the sleeve, a part of an outer peripheral surface of the sleeve and a part of an inner peripheral surface of the driven pulley. A one-way clutch that allows transmission of rotational force between the driven pulley and the sleeve only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction; Between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley, the one-way clutch is provided at a position displaced in the axial direction, and while supporting the radial load applied to the driven pulley, the sleeve and the driven pulley are connected to each other. In a pulley device with a built-in one-way clutch provided with a support bearing capable of relative rotation, a retainer for a clutch constituting the one-way clutch includes a sleeve and a driven pulley. The clutch retainer is configured to rotate with one of the two members. The both ends of the clutch retainer in the axial direction are provided on the other of the sleeve and the driven pulley or on the member that rotates with the other member. And a length in the axial direction between the pair of side surfaces is larger by 0.2 mm or more than the axial length of the clutch retainer. Pulley device with built-in one-way clutch.