JP2001349413A - Pulley device with built-in roller clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure strokes and to stabilize operations of leaf springs 41 and 41 for pressing rollers 16a even when axial dimension of the rollers 16a is shortened for miniaturizing. SOLUTION: Ridges 54 and 54 of folding parts 53 and 53 as displacement centers of elastic pieces 47 and 47 structuring respective leaf springs 41 and 41 are arranged in parallel with the center axis of a clutch holder 17c. Length of each of the elastic pieces 47 and 47 can be secured regardless of the axial length of each roller 16a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The roller clutch built-in pulley device according to the present invention comprises an alternator, a power steering oil pump, a water pump,
In order to drive auxiliary equipment such as a compressor for an air conditioner, it is used in a state where it is incorporated in a belt drive mechanism for rotationally driving each of these auxiliary equipments.

[0002]

2. Description of the Related Art Auxiliary equipment for an automobile is rotationally driven by a traveling engine of the automobile via a belt drive mechanism.
The structure of an alternator that is rotated and driven by a vehicle engine through such a belt drive mechanism and generates electric power necessary for the vehicle is described in, for example, JP-A-7-139550. FIG. 9 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 fixed to a portion of the rotating shaft 3 that protrudes outside the housing 2 at one end (the right end in FIG. 9). In an assembled state to the engine, an endless belt is stretched over the driven pulley 7 and the rotating shaft 3 is rotated by the crankshaft of the engine.
Is rotatable.

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 types of pulley devices with a built-in roller clutch that allow the driven pulley and the rotary shaft to rotate relative to each other have been proposed and used in part. 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 pulley device with a built-in roller clutch is described.
In some cases, such a pulley device with a built-in roller clutch is actually used.

[0004] FIG. 10 is a diagram showing Japanese Patent Application Laid-Open No. Hei 8-2264.
62 shows a pulley device with a built-in roller clutch described in JP-A-62. This pulley device with a built-in roller clutch has a sleeve 8 which can be fitted and fixed to the rotating shaft 3 of the alternator 1 (FIG. 9). A driven pulley 7 a is arranged around the sleeve 8 concentrically with the sleeve 8. A pair of support bearings 9, 9 are provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a.
And a roller clutch 10. The support bearings 9, 9 support the radial load applied to the driven pulley 7a, while supporting the sleeve 8 and the driven pulley 7a.
Relative rotation is free. Also, the roller clutch 1
A value of 0 enables the transmission of 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.

The outer peripheral surface of the intermediate portion of the inner ring 11 which constitutes the roller clutch 10 and is fitted and fixed to the sleeve 8 is
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 ring 15 that is fitted and fixed to the driven pulley 7a, which constitutes the roller clutch 10, is a simple cylindrical surface over substantially the entire length. or,
A plurality of rollers 16, 16 constituting the roller clutch 10 together with the inner ring 11 and the outer ring 15 are supported by a clutch retainer 17 rotating with the inner ring 11 so as to be able to roll and slightly displace in the circumferential direction. are doing. 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 diameter 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 in the form of inward flanges are provided at both axial ends of the outer ring 15. The axial inner side surfaces of the flanges 18, 18 are closely opposed to or abut on one axial end surfaces of the retainers 19, 19 constituting the support bearings 9, 9.

The reasons for using the pulley device with a built-in roller clutch as described above are as follows. The crankshaft of the traveling engine has fluctuations in the rotational angular velocity synchronized with the explosion.If the engine is a diesel engine or a direct injection gasoline engine, the rotational angular velocity of the crankshaft during low rotation, such as during idling, is reduced. Fluctuations are particularly large. 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 the driven pulley 7a, includes the rotating shaft 3, the rotor 5 fixed to the rotating shaft 3, and the commutator 6 (FIG. 9).
And does not fluctuate so rapidly. 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.

The above-described reduction in the power generation efficiency of the alternator and the reduction in the life of the endless belt due to the 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. Particularly, in the case of a vehicle equipped with an exhaust brake like a truck, the deceleration of the decrease in the 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 roller clutch is used as the driven pulley 7a as described above.
Accordingly, when the running speed of the endless belt is constant or increasing, the rollers 16, 16 constituting the roller clutch 10 move between the outer peripheral surface of the inner race 11 and the inner peripheral surface of the outer race 15. In the dimensions of the cylindrical gap formed in the above, the portion in which the width in the diametrical direction is narrowed is cut (locked), so that the rotational force can be freely transmitted from the driven pulley 7a to the rotary shaft 3. . 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.

Incidentally, leaf springs 20a and 20b as shown in FIGS. 11 to 12 are conventionally known as springs which are incorporated in the above-described roller clutch built-in pulley device and press the rollers 16 and 16. I have. The leaf springs 20a and 20b shown in FIGS.
No. 96090, which is formed by bending a metal spring plate.

A leaf spring 20a of the first example shown in FIG. 11 is formed by bending a spring plate into an "M" shape, and includes a flat base 21a and two ends of the base 21a. It has a pair of elastic pieces 22a, 22a bent at acute angles in directions approaching each other. Such a leaf spring 20a is
The base 21a is connected to the pillar 23a of the clutch holder 17a.
The roller 16 is pressed in the circumferential direction of the clutch retainer 17a by the tip of each of the elastic pieces 22a, 22a.

Further, the leaf spring 20b of the second example shown in FIG.
Is obtained by further folding a part of a spring plate bent in a U-shape, and includes a U-shaped base 21b and a pair of elastic pieces 22b, 22b folded from the center of one surface of the base 21b. Such a leaf spring 20b is formed in a state where the base 21b is externally fitted to the pillar 23b of the clutch holder 17b.
The roller 1 is formed by the distal ends of the elastic pieces 22b and 22b.
6 is pressed in the circumferential direction of the clutch retainer 17b.

[0012]

In the case of the conventional structure as described above, it is difficult to reduce the size and weight of the roller clutch built-in type pulley device due to the shape of the leaf springs 20a and 20b. For this reason, FIG.
4 will be described. In the case of the conventional structure shown in FIG.
The width W ₀ of the pulley device with a built-in clutch as a whole is considerably larger (W ₀ ≫W ₂₄ ) than the width W ₂₄ of the belt groove 24 for extending the endless driving belt. On the other hand, the pulley device with a built-in clutch needs to be installed in a limited space in the engine room, so it is necessary to manufacture the pulley device as small as possible. In particular, regarding the axial dimension, the fact that a part of the above-described clutch-incorporated pulley device protrudes from both end edges of the endless belt significantly impairs the degree of freedom in vehicle design, and improvement is desired.

The reason why the width W ₀ of the pulley apparatus with a built-in clutch is increased as described above is largely because the axial dimension L ₁₀ of the roller clutch ₁₀ is increased. In consideration of securing the capacity of the torque to be transmitted, the roller 1 constituting the roller clutch 10 is used.
It is necessary to increase the axial dimension of the roller 6 or to increase the outer diameter of the roller 16. Then, while ensuring the transmittable torque (torque capacity) by the roller clutch 10, in order to reduce the axial dimension L ₁₀ of the roller clutch 10, instead of reducing the axial dimension of the roller 16, It is necessary to increase the diameter of the roller 16.

When the axial dimension of the roller 16 is reduced from such a viewpoint, the above-described FIGS.
The dimension of the leaf springs 20a, 20b as shown in FIG. 12 in the axial direction of the clutch retainers 17a, 17b is also reduced. As in the conventional structure, in the case of a structure in which the ridge lines 27a and 27b of the bent portions serving as the displacement centers of the elastic pieces 22a and 22b are arranged in the diameter direction of the clutch retainers 17a and 17b, the leaf springs are used. If the dimensions of the leaf springs 20a and 20b are reduced, it becomes impossible to secure the lengths of the elastic pieces 22a and 22b constituting the respective leaf springs 20a and 20b. For example, the leaf spring 20a shown in FIG. 11 is changed from the shape shown in FIG. 13A to the shape shown in FIG. The leaf spring 20b changes from a shape as shown in FIG. 14A to a shape as shown in FIG.

As is apparent from a comparison between FIGS. 13A and 13B, FIGS.
In the case of 0b, if the dimension in the axial direction is reduced, the length of each of the elastic pieces 22a and 22b must be reduced. When the length of each of the elastic pieces 22a, 22b is reduced, the elastic pieces 22a, 22b are reduced.
The amount of elastic displacement of the leading end of the roller 16 decreases, and the roller 16 is moved in the circumferential direction of the roller clutch built-in type pulley device.
It cannot be pressed sufficiently.

On the other hand, Japanese Patent Application Laid-Open No. H11-82688 discloses a structure in which a roller constituting a roller clutch is pressed in a circumferential direction by a compression coil spring. According to such a structure, a sufficient pressing stroke can be ensured even for a roller having a large diameter and a small axial dimension. However, since the compression coil spring requires a large installation space in the circumferential direction of the roller clutch, the number of rollers that can be incorporated in the roller clutch decreases accordingly, and the torque capacity decreases. In order to shorten the axial dimension of the pulley device with a built-in roller clutch, if the diameter of each roller is increased by the amount of shortening the axial length of each roller, it can be installed if the diameter of the roller clutch is the same. The number of rollers is reduced. For this reason, when the number of rollers further decreases due to the installation of the spring, it becomes difficult to secure sufficient durability as a roller clutch built-in type pulley device for driving an auxiliary machine for an automobile. The present invention, in view of such circumstances, while securing the torque capacity,
The present invention has been devised to realize a roller clutch built-in type pulley device capable of reducing the axial dimension and securing a sufficient length for pressing a roller by a spring to stabilize an operation state.

[0017]

A pulley device with a built-in roller clutch according to the present invention, like a pulley device with a built-in roller clutch, has a sleeve which can be externally fitted and fixed on a rotating shaft, and a sleeve of this sleeve. Pulleys arranged concentrically with the sleeve are provided between a part of the outer peripheral surface of the sleeve and a part of the inner peripheral surface of the pulley, and the pulley has a tendency to rotate relative to the sleeve in a predetermined direction. Only when this occurs, the roller clutch that enables the transmission of rotational force between these pulleys and the sleeve, and this roller clutch is displaced in the axial direction between the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley. And a support bearing for supporting the radial load applied to the pulley and allowing the sleeve and the pulley to rotate relative to each other. The roller clutch includes a clutch retainer that rotates together with one of the sleeve and the driven pulley, a plurality of rollers rotatably held by the clutch retainer, and each of these rollers. And a plurality of leaf springs provided between the clutch retainer. In particular, in the roller clutch-incorporated pulley device of the present invention, each of the leaf springs has a base supported by the roller clutch retainer, and a distal end provided with the base end connected to the base. And an elastic piece provided with elasticity in a direction in which the portion faces each of the rollers. The ridgeline of the bent portion, which is a continuous portion of the elastic piece and the base and is the center of displacement of the elastic piece, is disposed substantially parallel to the central axis of the clutch retainer.

[0018]

According to the roller clutch built-in type pulley device of the present invention configured as described above, the axial dimension can be reduced.
In addition, it is possible to realize a pulley device with a built-in roller clutch that can secure a sufficient length for pressing the roller by the leaf spring and stabilize the operation state. That is, since the ridgeline of the bent portion serving as the displacement center of the elastic piece is disposed substantially parallel to the central axis of the clutch retainer, the length of the elastic piece is restricted by the axial dimension of the roller. Not receive. For this reason, in order to shorten the axial length of the roller clutch built-in type pulley device as a whole, even if the axial size of the rollers constituting the roller clutch is shortened, the operating length of the elastic piece is sufficiently secured, The operation state of the roller clutch can be stabilized.

[0019]

1 to 3 show a first embodiment of the present invention. The pulley device with a built-in roller clutch according to the present embodiment has a cylindrical shape as a whole, and a sleeve 8a that is externally fitted and fixed to an end of the rotating shaft 3 (see FIGS. 9 to 10) of the alternator. This sleeve 8
a) and a driven pulley 7b concentrically arranged. The sleeve 8a is rotatable with the rotation shaft 3. For this reason, in the illustrated example, a female screw portion 25 is formed on the inner peripheral surface of the intermediate portion of the sleeve 8a, and the female screw portion 25 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 25 and the male screw portion, a tip end portion of a tool such as a hexagon wrench is engaged with an inner peripheral surface of one end portion (left end portion in FIG. 1) of the sleeve 8a. A hexagonal hole 26 that can be stopped is formed.

The driven pulley 7b provided around the sleeve 8a has a pair of support bearings 28, 28 and a roller clutch 10a described below mounted inside the driven pulley 7b. or,
The belt bridging portion 29 provided on the outer peripheral surface of the driven pulley 7b has a cross-sectional shape in the width direction as a waveform, and is capable of bridging a part of an endless belt called a poly-V belt. Particularly, in the case of the driven pulley 7b constituting the roller clutch built-in type pulley apparatus of the present invention, as compared to the width (axial dimension) W ₂₉ of the belt receiving spanning portions 29, the proximal end of the pulley 7b ( an inner diameter side end portion) in the mounting support bearings 28, 28 and roller clutch 10a of the pair portion of the width (axial dimension) W _7b, is set to an extent that slightly larger.

In the case of this embodiment, a pair of support bearings 28, 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.
28 and one roller clutch 10a.
Each of the support bearings 28 includes an inner ring 31 having a deep groove type inner raceway 30 on the outer peripheral surface, an outer ring 33 having a deep groove type outer raceway 32 on the inner peripheral surface, and the inner raceway 30 and the outer raceway. And rolling elements (balls) 34, 34, each of which is provided so as to be able to roll freely. The outer ring 33 is fitted and fixed to the inner peripheral surface of the driven pulley 7b near both ends, and the inner ring 31 is fixed to the outer peripheral surfaces of both ends of the sleeve 8a by interference fitting. The outer peripheral surfaces of both ends of each inner ring 31 and each outer ring 3
3 between the inner peripheral surfaces of both ends.
5 and 35, the plurality of rolling elements 34,
In addition to preventing the entry of foreign matter into the space where 34 exists, the grease existing in each of the support bearings 28 and 28 is prevented from leaking to the outside.

Further, in order to constitute the roller clutch 10a, an inner ring 36 for the roller clutch is externally fitted and fixed to the outer peripheral surface of the axially intermediate portion of the sleeve 8a by interference fitting. The roller 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 roller clutch is fixedly fitted to the inner peripheral surface of the intermediate portion of the driven pulley 7b by interference fit. The outer ring 38 for the roller clutch is formed in a cylindrical shape as a whole by pressing a hard metal plate such as bearing steel or a carburized steel plate such as SCM415. In the case of the present embodiment, the flanges 18, 18 of the conventional structure shown in FIG. 10 are not provided at both ends of the outer ring 38 for the roller clutch. The reason for this is that, in order to secure the torque capacity of the roller clutch 10a, the plurality of rollers 16a constituting the roller clutch 10a,
This is to make the axial length of 16a as large as possible under limited conditions.

At a plurality of locations on the outer peripheral surface of the roller clutch inner ring 36, recesses 39, 39, called ramps, whose depth increases as going in a predetermined direction with respect to the circumferential direction.
Are formed at regular intervals in the axial direction and in the circumferential direction of the inner ring 36 for the roller clutch, and the outer peripheral surface of the inner ring 36 for the roller clutch is the cam surface 37. A cylindrical gap 40 is formed between the outer peripheral surface of the roller clutch inner ring 36 and the inner peripheral surface of the roller clutch outer ring 38. Of the dimensions of the cylindrical gap 40, The width of the outer ring 38 and the inner ring 36 for the roller clutch in the diametrical direction is determined by the outer diameter of the plurality of rollers 16a, 16a provided in the cylindrical gap 40 at the portion corresponding to the deepest portion of each of the recesses 39, 39. D ₁₆ greater than, the deviated portion from the respective recesses 39, 39 each of these rollers 16a, 16a of the outer diameter D ₁₆
Less than.

The roller clutch 10a is provided between the inner peripheral surface of the outer ring 38 for roller clutch and the outer peripheral surface of the inner ring 36 for roller clutch. And a plurality of the rollers 16a, 16a, and a leaf spring 4 which is a characteristic portion of the pulley device with a built-in roller clutch of the present invention.
1 and 41 are provided. The clutch retainer 17c includes a pair of rims 42 each having an annular shape.
42, and a plurality of pillars 43, 43 connecting the two rims 42, 42 to each other. Then, each of the rim portions 4
A portion surrounded by four sides by the inner side surfaces of 2, 42 and the side surfaces of the respective column portions 43, 43 is used for rolling the respective rollers 16a, 16a and holding the rollers 16a, 16a freely displaceable in the circumferential direction. A plurality of pockets 44 are provided. By engaging the convex portions 45, 45 formed at a plurality of locations on the inner peripheral surface of the rim portions 42, 42 with the concave portions 39, 39 formed on the outer peripheral surface of the roller clutch inner ring 36, the clutch For the roller clutch inner ring 3
6, the roller clutch inner ring 36 is mounted so as not to rotate relative to the inner ring 36. Also, each of the leaf springs 41, 41
Is provided between the pillars 43, 43 constituting the clutch retainer 17c as described above and the rollers 16a, 16a, and these rollers 16a, 16a are arranged in the same direction in the circumferential direction (FIG. 2). To the left).

Each of the leaf springs 41, 4 which is a feature of the present invention.
1, in the case of this example, a spring steel having a thickness of about 0.1 to 0.2 mm is formed by bending, and the base 46 and the pair of elastic pieces 4 are formed.
7 and 47 are used. The base portion 46 includes a substrate portion 48 abutting on the outer peripheral surface of each of the pillar portions 43, 43, and one end edge (right end edge in FIGS. 2 to 3) of the substrate portion 48 in the circumferential direction. Over
The first holding plate portion 49 bent inward in the radial direction, and the first holding plate portion 49 bent radially inward from the center of the other end edge (left end edge in FIGS. 2 to 3) of the substrate portion 48 in the circumferential direction. And a second holding plate portion 50.

The first and second holding plates 49, 5
Locking protruding portions 51, 51 protruding in directions approaching each other are formed at the distal end (the inner diameter side end) of the zero. In a state where the respective leaf springs 41, 41 are mounted on the respective column portions 43, 43, the substrate portion 48 comes into contact with the outer peripheral surfaces of the respective column portions 43, 43, and the respective locking projections 51, 51 A locking step 5 formed at a radially intermediate portion on both sides of each of the pillars 43, 43;
2, 52 are engaged. Therefore, regardless of the centrifugal force applied during use, each of the leaf springs 41, 41
It does not fall off from 3 radially outward. The outer peripheral surface of each of the pillars 43 is slightly (substantially equivalent to the thickness of the substrate 48) radially inward of the outer peripheral edge of each of the rims 42, 42. Therefore, the board portion 48 does not protrude radially outward from the outer peripheral edges of the rim portions 42, 42, and the board portion 48 and the clutch outer ring 38 do not protrude.
Of the clutch outer race 38 is not damaged.

On the other hand, each of the elastic pieces 47, 47 is bent radially inward from a portion near both ends of the other end of the substrate portion 48. The amount of bending is smaller than that of the second holding plate portion 50. Therefore, the respective elastic pieces 47, 47 are kept in a state where the respective leaf springs 41, 41 are in contact with the respective column portions 43, 43.
Are separated from the side surfaces of the pillars 43.
The ridges 54, 54, which are continuous portions of the elastic pieces 47, 47 and the base 46, and serve as the centers of displacement of the elastic pieces 47, 47, are connected to the clutch holder 17c. Are arranged substantially in parallel with the central axis of. In this state, each of the elastic pieces 47, 47
Is oscillatingly displaced around the bent portions 53, 53,
Each of the rollers 16a, 16a
Toward the narrow portion of the cylindrical gap 40 with, for example, about 0.3 to 0.6 N for each roller 16a.

In the illustrated example, the projections 45 formed on the inner peripheral edges of the rims 42, 42 constituting the clutch retainer 17c and engaged with the recesses 39, 39, respectively.
The outer surface of the driven pulley 7b of the clutch retainer 17c is brought into contact with or close to the end surfaces of the inner rings 31, 31 constituting the support bearings 28, 28.
In the axial direction. At the same time, in the case of this example, the outer diameter side half of the outer surface of each of the rim portions 42, 42 is slightly depressed inward in the axial direction (for example, about 0.5 mm), and this portion and each of the support members are depressed. The end faces of the outer rings 33, 33 constituting the bearings 28, 28 are prevented from rubbing against each other. Therefore, when the connection of the roller clutch 10a is disconnected and the driven pulley 7b and the sleeve 8a relatively rotate, so-called overrun, the outer surfaces of the rims 42 and 42 and the end surfaces of the outer races 33 and 33 are in contact with each other. Rubbing can be prevented, so that resistance for overrun can be prevented from increasing or heat generation can be prevented from increasing.

In the pulley device with a built-in roller clutch of the present invention constructed as described above, the roller clutch 10a includes the driven pulley 7b in which the outer ring 38 for roller clutch is fixed and the rotating shaft 3 in which the sleeve 8a is fixed. , Only the rotational force in the predetermined direction is transmitted. For example, assuming that the roller clutch inner ring 36 is fixed and only the roller clutch outer ring 38 rotates in FIG. 2, when the roller clutch outer ring 38 rotates clockwise in FIG. The rollers 16a, 16a are the outer races 38 for the roller clutch.
Each of the leaf springs 41, 4 based on the force received from the inner peripheral surface of the
As shown by the solid line in FIG. 2, the concave portions 39, 39 tend to be displaced toward the deeper side against the elasticity of 1. The rollers 16a, 16a are connected to the cylindrical gap 4
Rolling is possible within 0, and an overrun state occurs in which the transmission of rotational force is not performed between the roller clutch outer ring 38 and the roller clutch inner ring 36.

On the other hand, when the outer ring 38 for roller clutch rotates counterclockwise in FIG.
As shown by a chain line in FIG. 2, the recesses 39, 39 become shallower based on the force received by the inner peripheral surface of the roller clutch outer ring 38 and the elasticity of the leaf springs 41, 41a. Bite into the wedge. The roller clutch outer ring 38 and the roller clutch inner ring 36 are integrally connected to each other, so that the rotational force can be freely transmitted between the roller clutch outer ring 38 and the roller clutch inner ring 36, a so-called lock. State.

In order to realize such a locked state, the respective elastic pieces 47, 4 constituting the respective leaf springs 41, 41 are required.
7, the respective rollers 16a, 16a are connected to the respective concave portions 39,
It is necessary to securely push down to the portion where 39 becomes shallow. In the case of the roller clutch built-in pulley device of the present invention, the ridge lines 54, 54 of the bent portions 53, 53, which are the centers of displacement of the elastic pieces 47, 47, are substantially aligned with the central axis of the clutch retainer 17c. Are arranged parallel to each other, even when the axial dimension of each of the rollers 16a, 16a is short, the amount of displacement of the tip of each of the elastic pieces 47, 47 (these rollers 16a, 16a are connected to the respective concave portions 39). , 39) can be sufficiently secured.

That is, in the case of the conventional leaf springs 20a and 20b as shown in FIGS.
The length of the roller 22b cannot be made more than の of the axial dimension of the roller 16. On the other hand, in the case of the present invention, the length of the elastic pieces 47, 47 constituting the respective leaf springs 41, 41 is
It can not be more than the outer diameter D ₁₆ of the rollers 16a. Therefore, when considering the ratio between the axial dimension L ₁₆ and the outer diameter D ₁₆ of the rollers 16, 16a, the axial dimension L ₁₆ is the outer diameter D
_In the case of {(L ₁₆ / D ₁₆ ) <2} less than twice of ₁₆ , the length of the elastic piece for pressing the roller 16a is longer in the structure of the present invention than in the conventional structure, The above stroke can be secured. The present invention has an outer diameter D ₁₆ of the roller 16a is 2.
If it is 5 mm or more, it can be implemented sufficiently. Of course larger the the outer diameter D ₁₆ is increased, the effect of the present invention becomes remarkable.

In the pulley device with a built-in roller clutch according to the present invention, the overrun state and the locked state are repeated as described above, so that the endless belt stretched over the driven pulley 7b and the rubbed portion of the driven pulley 7b. The direction of the stress acting on the endless belt is kept constant 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 rotation shaft 3 of the alternator is fixed to the rotation shaft 3 itself and the rotor 5 fixed to the rotation shaft 3.
Based on the rotational inertia force of the motor and the commutator 6 (FIG. 9) and the like, the motor can be continuously rotated at a certain high speed, and the power generation efficiency of the alternator can be improved.

In particular, the roller clutch built-in pulley of the present invention
According to the re-apparatus, before the respective leaf springs 41, 41 are configured.
A bent portion 5 serving as a displacement center of each elastic piece 47, 47
The ridge lines 54, 54 of the clutch retainers 1, 3
7c is arranged substantially parallel to the central axis.
The length of each elastic piece 47 is equal to the axis of the roller 16a.
It is not restricted by directional dimensions. Because of this,
In order to shorten the axial length of the pulley device with built-in
Each roller 16a, 1 constituting the roller clutch 10a
Even if the axial dimension of 6a is shortened (the rollers 16a, 16a
Axial dimension L ₁₆Is the outer diameter D₁₆Less than twice)
The operating length of each elastic piece 47, 47 is sufficiently secured, and
It is possible to stabilize the operation state of the roller clutch 10a.
Wear.

The above description has been made in the case where the pulley device with a built-in roller clutch of the present invention is embodied as a driven pulley device provided at an end of a rotating shaft of an alternator. The type pulley device is
It can also be used by incorporating it into a belt drive mechanism for driving auxiliary equipment other than the alternator, such as an oil pump for power steering, a water pump, and a compressor for an air conditioner. Further, the present invention can be implemented not only in combination with a driven pulley mounted on the rotating shaft side of each of these accessories, but also in combination with a drive pulley mounted on the crankshaft side of the traveling engine. That is, even if a roller clutch is incorporated in the drive pulley portion and the roller clutch is connected (locked) only when the rotation speed of the crankshaft is equal to or higher than the rotation speed corresponding to the traveling speed of the belt, The above-described functions and effects such as improvement in durability can be obtained. Further, the present invention is not limited to a diesel engine or a direct-injection gasoline engine as a traveling engine, but similar effects can be obtained even when applied to a normal gasoline engine, although the degree is different.

Therefore, it is preferable that the installation position of the pulley device with a built-in roller clutch according to the present invention is selected from among the installation positions of the driven pulley or the driving pulley, where a relatively large space is available. The reason is that the roller clutch built-in type pulley device of the present invention is smaller and smaller than the aforementioned conventional structure.
Although it is possible to reduce the weight, it is inevitable to increase the size compared to a fixed type pulley (as shown in FIG. 9) having no roller clutch or support bearing. Therefore, if a fixed pulley is provided in a place where there is no room for space, and the pulley device with a built-in roller clutch of the present invention is installed in a place where there is room for space, the design of the pulley device with a built-in roller clutch can be improved. The degree of freedom is improved, and the durability of the pulley device can be easily ensured.

Next, FIGS. 4 to 6 show a second example of the embodiment of the present invention. Leaf springs 41a, 4 incorporated in this example
1a, the elastic piece 47a is formed over the entire width thereof. For this reason, the base 46 constituting each of these leaf springs 41a is provided.
“a” forms first and second holding plate portions 49 and 50a that are bent radially inward over the entire width from both end edges in the circumferential direction of the substrate portion 48, respectively. The shape of the first holding plate portion 49 is the same as that of the first example described above, but the second holding plate portion 50a has a step portion 55 formed at a radially intermediate portion. The step 55 is engaged with a locking step 52 formed on the side surface of the pillars 43 constituting the clutch retainer 17c.

The elastic piece 47a is bent at an acute angle from the inner diameter side edge of the second holding plate portion 50a to the outer diameter side. The elastic piece 47a is provided with elasticity in a direction to increase the angle of the bent portion 53a which is a continuous portion with the second holding plate portion 50a, and the distal end portion of the elastic piece 47a moves the roller 16a to the cylindrical space. The portion 40 is elastically pressed against a portion having a reduced width in the diameter direction. The leaf springs 41a and 41 having such a shape and incorporated in the present example.
Since a is formed over the entire width of the second holding plate portion 50a and the elastic piece 47a, even when the width dimension is reduced as the axial dimension of the roller 16a is reduced,
The work of forming the second holding plate portion 50a and the elastic piece 47a can be easily performed.

The elastic piece 47a shown by a chain line in FIG.
As is apparent from a comparison between the free state and the elastically compressed state shown by the solid line in the figure, the elastic piece 47a caused the roller 16a to have a component force directed radially inward. In the state, press in the circumferential direction. Therefore, before the roller clutch inner ring 36 is inserted into the inner diameter side of the clutch retainer 17c, the roller 16a is connected to one side surface (the right side surface in FIG. 5) of the pillar portion 43 constituting the clutch inner ring 17c. Is pressed against the inclined surface portion 56 provided at the bottom. For this reason, the outer ring 38a for the roller clutch and the retainer 1 for the clutch are used.
7c, the leaf springs 41a, 41a and the roller 16a are assembled, and even before the roller clutch inner ring 36 is assembled, the roller 16a may be accidentally dropped on the inner diameter side of the clutch retainer 17c. Absent. Therefore, the assembly work of the roller clutch 10b can be easily performed.

Since the distal end edge of the elastic piece 47a faces the outer diameter side, the roller 16a is inserted into the clutch retainer 17c previously assembled on the inner diameter side of the clutch outer ring 38a. When assembling from the inner diameter side of the retainer 17c, the rolling surface of the roller 16a does not collide with the leading edge of the elastic piece 47a. Therefore, the assembling work of the roller 16a can be easily performed without damaging the rolling surface of the roller 16a,
When assembling the roller 16a, the leaf springs 41a,
1a does not accidentally fall off the pillars 43, 43. Therefore, from the viewpoint of facilitating the work of assembling the roller 16a, the efficiency of the work of assembling the roller clutch 10b can be improved.

In the present embodiment, unlike the first embodiment, inward flange-like flanges 18a, 18a are provided at both ends of a roller clutch outer ring 38a constituting the roller clutch 10b. ing. Such a flange portion 18a,
18a, the outer ring 3 for the roller clutch is provided.
The lubricant such as grease existing on the inner peripheral surface of the roller clutch 8a is less likely to flow to the outside, and the lubricity of the roller clutch 10b is improved. Outer ring 38a for such a roller clutch
Is made of a plate material made of carburized steel such as SCM415, and after pressing this plate material to form a cylindrical shape having the flanges 18a, 18a at both ends thereof,
The surface is hardened by carbonitriding and quenching. The outer surfaces of the flanges 18a, 18a, which are both end surfaces in the axial direction of the outer ring 38a for the roller clutch, constitute support bearings 28, 28, respectively.
The inner peripheral surface of the outer ring 33 is in contact with or close to the inner end surface of each of the outer races 33, 33 which are fitted and fixed to the axially opposite ends of the inner peripheral surface.

In the case of this embodiment, the clutch retainer 1
7c, the outer diameter of the pair of rim portions 42a, 42a
Inner diameter of each of the flanges 18a, 18a (further, inner diameter of the end faces of the outer rings 33, 33 constituting the respective support bearings 28, 28)
And the rims 42a, 42a are located on the inner diameter side of the flanges 18a, 18a.
In addition, the axial dimension of the clutch retainer 17c is made slightly larger (for example, about 0.5 to 1 mm) than the axial dimension of the roller clutch outer ring 38a, so that each of the rim portions 42 is formed.
A part of a, 42a is made to protrude slightly from the outer surface of each of the flanges 18a, 18a. In this case,
The outer surfaces of the rim portions 42a, 42a and the outer rings 3
The end faces of 3, 33 do not rub against each other.

By configuring the clutch retainer 17c and the roller clutch outer ring 38a as described above, it is possible to secure the torque capacity of the roller clutch 10b and to facilitate the manufacturing operation. The torque capacity can be ensured by increasing the axial dimension of the clutch retainer 17c and maximizing the axial dimension of the roller 16a within a limited space.

In addition, the facilitation of the manufacturing operation is achieved by the
a, the outer ring 38a for the roller clutch on which the 18a is formed.
The clutch retainer 17c and the roller 16
a, 16a. That is, the outer diameter of each of the rims 42a, 42a is
8A and 18A are smaller than the inner diameter of FIG.
As shown in (A) to (C), the clutch retainer 17c to which a leaf spring is attached in advance and the rollers 16a, 16a are assembled on the inner diameter side of the roller clutch outer ring 38a. Therefore, the flanges 18 are provided at both ends in the axial direction.
a, the roller clutch outer ring 38a provided with 18a
Can be made all at once by pressing. As a result, the manufacturing operation of the outer ring 38a for the roller clutch can be simplified, and the cost of the roller clutch 10b including the outer ring 38a for the roller clutch can be reduced.
The roller 16a can be easily inserted from the inner diameter side of the clutch retainer 17c without damaging the rolling surface thereof. This is because the elastic piece 4 of the leaf spring 41a
This is because the leading edge of 7a faces the outer diameter side.

On the other hand, as in the conventional structure shown in FIG. 10, the clutch retainer 17 is arranged between the flanges 18 formed at both ends of the outer ring 15 for the roller clutch. In this case, as shown in FIGS.
Since it is necessary to form the collar 18 after the clutch retainer 17 and the roller 16 to which a leaf spring is attached in advance on the inner diameter side of the roller clutch outer ring 15, the pressing process of the roller clutch outer ring 15 is required. Is performed twice, which makes the processing operation troublesome and increases the cost. The structure of the second example shown in FIG. 4 can reduce such a trouble and reduce the cost.

The other constructions and operations are the same as those in the first example described above, and therefore, duplicate explanations will be omitted. In the illustrated embodiments, the support bearing 28,
Although a deep groove type ball bearing is used as 28, the structure of the support bearing is not particularly limited when the present invention is implemented. A needle bearing as shown in FIG. 10 described above, a combination of a needle bearing and a ball bearing, or the like may be employed.

[0047]

The pulley device with a built-in roller clutch according to the present invention is constructed and operates as described above, so that a pulley device with a built-in roller clutch that is small and lightweight and has a stable operation state can be realized.

[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 a perspective view of a leaf spring.

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

FIG. 5 is an enlarged cross-sectional view taken along the line BB of FIG.

FIG. 6 is a perspective view of a leaf spring.

FIG. 7 is a partial schematic cross-sectional view showing an assembling operation of a roller clutch incorporated in the second example in the order of steps.

FIG. 8 is a view similar to FIG. 7, showing a case of a conventional structure.

FIG. 9 is a sectional view showing an example of a conventionally known alternator.

FIG. 10 is a sectional view showing an example of a conventionally known pulley device with a built-in roller clutch for an alternator.

FIG. 11 is a partial perspective view of a roller clutch, showing a first example of a conventional leaf spring.

FIG. 12 is a partial perspective view of a roller clutch showing the second example.

FIG. 13 is a cross-sectional view showing a first example of a conventional leaf spring in a state where dimensions in the axial direction of a retainer for a clutch are different from each other.

FIG. 14 shows a case of the leaf spring of the second example,
FIG.

[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, 10b Roller clutch 11 Inner ring 12 Depression 13 Cam surface 14 Inner ring raceway 15 Outer ring 16, 16a Roller 17, 17a, 17b, 17c Clutch retainer 18, 18a Flange 19 Retainer 20a, 20b Leaf spring 21a, 21b Base 22a, 22b Elastic piece 23a, 23b Column 24 Belt groove 25 Female thread 26 Hexagon hole 27a, 27b Ridge line 28 Support bearing 29 Belt bridge portion 30 Inner raceway 31 Inner raceway 32 Outer raceway 33 Outer raceway 34 Rolling element 35 Seal ring 36 Inner raceway for roller clutch 37 Cam surface 38, 38a Outer raceway for roller clutch 39 Recess 40 Cylindrical gap 41 , 1a Leaf spring 42, 42a Rim 43 Column 44 Pocket 45 Convex 46, 46a Base 47, 47a Elastic piece 48 Board 49 First holding plate 50, 50a Second holding plate 51 Locking projection Part 52 Locking step part 53, 53a Bent part 54, 54a Ridge line 55 Step part 56 Inclined surface part

Claims (1)

[Claims] 1. A sleeve which can be externally fitted to and fixed to a rotating shaft, a pulley disposed concentrically with the sleeve around the sleeve, a part of an outer peripheral surface of the sleeve and a part of an inner peripheral surface of the pulley. A roller clutch which is provided between the pulley and the sleeve so as to freely transmit a rotational force between the pulley and the sleeve only when the pulley tends to rotate relative to the sleeve in a predetermined direction; and an outer peripheral surface of the sleeve. A roller bearing is provided at a position axially displaced from the roller clutch between the roller and the inner peripheral surface of the pulley, and a support bearing that supports the radial load applied to the pulley and allows relative rotation between the sleeve and the pulley. The roller clutch includes a clutch retainer that rotates together with one of the sleeve and the driven pulley, and a plurality of roller clutches rotatably held by the clutch retainer. And a plurality of leaf springs provided between each of these rollers and the clutch retainer. A base supported by the retainer, and an elastic piece provided with elasticity in a direction in which a front end thereof is directed toward each of the rollers in a state where the base end is connected to the base. A ridge line of a bent portion which is a continuous portion of the elastic piece and the base and serves as a center of displacement of the elastic piece is arranged substantially parallel to a central axis of the clutch retainer. Pulley device with built-in roller clutch.