JP2001041314A - Pulley device with built-in one-way clutch for alternator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a follower pulley from axially shifting with reference to a sleeve, and to reduce a processing cost of the follower pulley by forming the inner peripheral surface of the follower pulley in a single cylindrical surface. SOLUTION: Caulking portions 30, 30 are formed in a both end surfaces inner periphery part of a follower pulley 7b, and the outer end surface of each of bearing inner rings 19, 19 composing a pair of support bearings 10, 10 is suppressed by the caulking portions 30, 30. Therefore, the follower pulley 7b is prevented from axially shifting with reference to a sleeve 8a. Accordingly, a stepped surface conventionally formed on the inner peripheral surface of the follower pulley 7b is eliminated, and the inner peripheral surface of the follower pulley 7b is formed in a single cylindrical surface.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

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

Conventionally, the driven pulley 7 is generally
What was simply fixed to the rotating shaft 3 was used. On the other hand, in recent years, when the traveling speed of the endless belt is constant or increasing, transmission of power from the endless belt to the rotating shaft is freely performed, and when the traveling speed of the endless belt tends to decrease, Various pulley devices with a built-in one-way clutch for alternators, which make the relative rotation between the driven pulley and the rotary shaft freely, have been proposed and used in part. For example, JP-A-56-101353, JP-A-7-3
No. 17807, No. 8-61443, No. 8-2
No. 26462, No. 11-63026, Japanese Patent Publication No. 7-72585, French Patent Publication FR2726
059A1 and the like describe a pulley device with a built-in one-way clutch for an alternator having the above-described functions.

[0004] FIG.
1 shows a pulley device with a built-in one-way clutch for an alternator, which is described in Japanese Patent Application Laid-Open Publication No. H11-209,878. This one-way clutch built-in pulley device for an alternator has a sleeve 8 which can be fitted and fixed to the rotating shaft 3 (FIG. 5) of the alternator 1.
A driven pulley 7 a is arranged around the sleeve 8 concentrically with the sleeve 8. This driven pulley 7
The outer peripheral surface of “a” has a cross-sectional shape in the width direction as a waveform, and allows a part of an endless belt 32 called a poly V belt to be freely passed over. Then, the one-way clutch 9 is provided at an intermediate portion in the axial direction of the space existing between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a, and the one-way clutch 9 is similarly provided at both ends of this space. A pair of support bearings 10, 10 are provided at positions sandwiched from both sides in the axial direction. Among these, the support bearings 10 and 10 allow the driven pulley 7a and the sleeve 8 to rotate relative to each other while supporting the radial load applied to the driven pulley 7a. The one-way clutch 9 is connected to the driven pulley 7a.
Only when the roller 8 tends to rotate relative to the sleeve 8 in a predetermined direction, the driven pulley 7a
Transmission of rotational force to the motor.

The one-way clutch 9 comprises a clutch inner ring 1 which is externally fitted and fixed to an axially intermediate portion of the sleeve 8.
A plurality of concave portions 12 called a ramp portion
Are formed at regular intervals in the circumferential direction, and the outer peripheral surface is a cam surface 13. On the other hand, on the inner peripheral surface of the second sleeve 14 constituting the inner diameter side portion of the driven pulley 7a, an intermediate portion diametrically opposed to the cam surface 13 is a cylindrical surface 15
And A plurality of rollers 16 constituting the one-way clutch 9 together with the clutch inner ring 11 and the cylindrical surface 14 are attached to a synthetic resin clutch retainer 17.
The roller is supported so as to be freely displaceable in the rolling and circumferential directions. In the illustrated example, a part of the clutch retainer 17 is replaced with the clutch inner race 11 and a bearing inner race 19 described below.
, The rotation of the clutch retainer 17 with respect to the clutch inner race 11 is disabled. A spring is provided between the column provided on the clutch retainer 17 and each of the rollers 16, and these rollers 16, 16 are elastically pressed in the same direction with respect to the circumferential direction.

In the illustrated example, each of the above-described support bearings 1 is provided.
As 0 and 10, deep groove ball bearings are used. That is, each of these support bearings 10, 10 has a bearing inner ring 19, 19 having a deep groove type inner raceway 18, 18 on each outer peripheral surface, and a deep groove type outer raceway 20, 20 on each inner peripheral surface. The bearing comprises outer races 21, 21 for bearings, and balls 22, 22, which are provided between the inner raceways 18, 18 and the outer raceways 20, 20, respectively, so as to freely roll. In the assembled state shown in the drawing, each of the bearing inner rings 1
9 and 19 are externally fitted and fixed to both ends of the outer peripheral surface of the sleeve 8 by interference fit, respectively, and the bearing outer rings 21 and 21 are respectively attached to both ends of the inner peripheral surface of the second sleeve 14. It is fitting. Further, in this state, the inner surfaces of the bearing outer rings 21 and 21 (the one-way clutch 9
Side surfaces) are brought close to or in contact with the step surfaces 23 formed on the inner peripheral surface of the second sleeve 14, respectively. Thus, even when a thrust load (a load extending in the axial direction) is applied to the driven pulley 7a, the driven pulley 7a is prevented from being largely displaced in the axial direction.

The reason for using the pulley device with a built-in one-way clutch for an alternator as described above is as follows. For example, when the driving engine is a diesel engine, the rotation angular speed of the crankshaft greatly fluctuates during low rotation such as during idling. As a result, the running speed of the endless belt 32 stretched 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 32 via a driven pulley is composed of the rotating shaft 3, the rotor 5 fixed to the rotating shaft 3, and the inertial mass of the commutator 6 (FIG. 5). Does not fluctuate so rapidly. Therefore, when the driven pulley is simply fixed to the rotating shaft 3, when the running speed of the endless belt 32 decreases, the rotating speed of the rotating shaft 3 decreases as it is, and the power generation amount of the alternator 1 decreases. At the same time, the inner peripheral surface of the endless belt 32 and the outer peripheral surface of the driven pulley tend to rub in both directions with the fluctuation of the rotational angular speed of the crankshaft. As a result, stresses in different directions are repeatedly applied to the endless belt 32 that rubs against the driven pulley, so that the endless belt 32 is likely to slip between the endless belt 32 and the driven pulley, or the life of the endless belt 32 is reduced. May be shortened. Such a reduction in the amount of power generated by the alternator 1 and a reduction in the life of the endless belt 32 due to friction between the outer peripheral surface of the driven pulley and the inner peripheral surface of the endless belt 32 also occur due to repeated acceleration and deceleration during traveling. .

Therefore, by using the pulley device with a built-in one-way clutch for the alternator as the driven pulley as described above, when the running speed of the endless belt 32 is constant or tends to increase, the driven pulley is used. When the running speed of the endless belt 32 tends to decrease, the relative rotation between the driven pulley and the rotating shaft 3 is made freely. That is, when the traveling speed of the endless belt 32 tends to decrease, the rotational angular speed of the driven pulley is made slower than the rotational angular speed of the rotating shaft 3 so that the contact portion between the endless belt 32 and the driven pulley is reduced. To prevent strong rubbing. In this way, the direction of the stress acting on the rubbed portion between the driven pulley and the endless belt 32 is kept constant, and slippage occurs between the endless belt 32 and the driven pulley, or the endless belt 32 Prevents shortening of service life. At the same time, even when the rotation speed of the engine is reduced, the rotation speed of the rotor of the alternator is prevented from being reduced, so that good power generation efficiency can be maintained.

When the conventional structure shown in FIG. 6 is implemented, the bearing outer races 21 are not fitted and fixed to the inner peripheral surface of the second sleeve 14 by interference. It is considered preferable to fit by gap fitting. The reason is as follows. That is, the bearing inner races 19, 19 or the bearing outer races 21, 21 constituting the support bearings 10, 10 are fitted and fixed to the outer peripheral surface of the sleeve 8 or the inner peripheral surface of the driven pulley 7a by interference fit. Then (when the fitting portion of each member has a large interference), the bearing inner rings 19, 19 or the bearing outer rings 21, 21 are elastically deformed in the diametric direction, and the bearing inner rings 19, 19 or the bearings are deformed. The diameter of the inner raceway 18, 18 or the outer raceway 20, 20 formed on the peripheral surface of the outer race 21, 21 changes (the diameter increases in the case of the inner raceway 18, and decreases in the case of the outer raceway 20). Become). As a result,
The radial internal gap of the support bearings 10 and 10 after assembly is reduced.

In this case, the amount of change in the diameter of the inner raceways 18, 18 or the outer raceways 20, 20 depends on the size of the interference of the fitting part (specifically, the fitting part). It is about 0.8 times as large as the interference.) For this reason, if the interference of this fitting portion becomes large, the inner raceway 18, 18
Alternatively, the amount of change in the diameter of the outer raceways 20, 20 also increases (at a rate of about 0.8). Also, left and right support bearings 9,
9 (the ratio of the amount of shrinkage to the interference of the fitting portion) of each of the bearing outer races 21, 21, and the respective bearing inner races 1.
If the expansion rates (the ratio of the expansion amount and the interference of the fitting portion) of the components 9 and 19 are the same, the variation of the diameter variation after assembling is determined by the variation of the interference of each of the fitting portions. The average value of the size of the interference at each fitting portion and the variation of the diameter change amount should be independent. But usually
Since the mating peripheral surfaces (the inner peripheral surface of the driven pulley 7a and the outer peripheral surface of the sleeve 8) fitting with the left and right support bearings 9, 9 are different from each other, the respective outer races 21 for the bearings are different. , 21 and the inner rings 19, 19
Is different from the expansion coefficient of the left and right support bearings 9,
The difference in the amount of change in the internal gap between the 9 is also large. In this case, if the support bearings 9, 9 having different initial gaps are selected and used according to the amount of change in the internal gap between the left and right support bearings 9, 9, the mutual difference as described above is obtained. However, since this method increases the assembly cost, the left and right support bearings 9,
No. 9 selects and uses the same initial gap division. For this reason, as described above, the difference between the internal clearances of the two support bearings 9 after assembly increases as the average value of the interference in each of the fitting portions increases.

In this case, the support bearings 10, 10
If the internal clearance in the radial direction becomes larger than an appropriate value, the driven pulley 7a will be eccentric with respect to the sleeve 8 when the one-way clutch 9 is locked, and the driven pulley 7a will swing. Conversely, if the internal clearance is smaller than an appropriate value, the durability of each of the support bearings 10 and 10 is impaired. Also, when a difference occurs in the size of the internal gap in the radial direction between the two support bearings 10, 10, the center axis of the cam surface 13 and the cylindrical surface 15 is inclined (not parallel), and A problem arises in that the rolling surfaces of the rollers 16, 16 are one-sided against the surfaces 13, 15. Any of these inconveniences are undesirable because they cause the life of the pulley device to be shortened.

Therefore, when the above-described conventional structure is implemented, the bearing outer rings 21 and 21 are fitted to the inner peripheral surface of the second sleeve 14 by gap fitting, respectively. It is considered preferable that the diameters of the outer raceways 20, 20 formed on the inner peripheral surfaces of the bearing outer races 21, 21 remain unchanged. Thereby, the dispersion of the radial internal gap of each of the support bearings 10 and 10 after assembly is reduced, and the internal gap is set to an appropriate value, or the internal clearance between the two support bearings 10 and 10 is reduced. It is considered that the mutual difference can be prevented from occurring.

[0013]

When the conventional pulley device with a built-in one-way clutch for an alternator as described above is implemented, each of the bearing outer rings 21, 21 constitutes an inner diameter side portion of the driven pulley 7a. It is preferable that the second sleeve 14 is fitted to the inner peripheral surface of the second sleeve 14 by gap fitting. Accordingly, a mechanism for preventing the driven pulley 7a from moving in the axial direction with respect to the sleeve 8 is required. On the other hand, in the case of the conventional structure shown in FIG. 6, a pair of step surfaces 23, 23 is formed on the inner peripheral surface of the second sleeve 14, and these step surfaces 23, 23 The outer races 21 are close to or in contact with the axially inner end faces of the outer races 21. However, forming such step surfaces 23, 23 is not preferable because it causes an increase in the processing cost of the driven pulley 7a. Therefore, by forming the inner peripheral surface of the driven pulley 7a into a single cylindrical surface over the entire length in the axial direction, the driven pulley 7a
It is desired to realize a structure capable of preventing the driven pulley 7a from moving in the axial direction with respect to the sleeve 8 while reducing the processing cost of the driven pulley. The pulley device with a built-in one-way clutch for an alternator of the present invention was invented in view of the above-mentioned circumstances.

[0014]

The pulley apparatus with a built-in one-way clutch for an alternator according to the present invention has a sleeve which can be externally fitted and fixed to the rotating shaft of the alternator, and has a sleeve around the sleeve. A driven pulley concentric with the sleeve is provided between an axially intermediate portion of the outer peripheral surface of the sleeve and an axially intermediate portion of the inner peripheral surface of the driven pulley, and the driven pulley is positioned relative to the sleeve in a predetermined direction. A one-way clutch that allows the transmission of rotational force between these driven pulleys and the sleeve only when it tends to rotate, and an outer circumferential surface of the sleeve at a position sandwiching the one-way clutch from both axial sides. A pair of support members provided between the inner peripheral surface of the driven pulley and supporting the radial load applied to the driven pulley and allowing relative rotation between the sleeve and the driven pulley. And a door bearing. Each of the support bearings has an outer raceway on the inner peripheral surface, a bearing outer race fitted on the inner peripheral surface of the driven pulley, an inner raceway on the outer peripheral surface, and an outer raceway on the outer peripheral surface of the sleeve. It comprises a bearing inner ring to be fitted, and a plurality of rolling elements rotatably provided between the outer raceway and the inner raceway.

In particular, in the pulley device with a built-in one-way clutch for an alternator according to the present invention, each of the bearing inner rings is externally fitted and fixed to both ends of the outer peripheral surface of the sleeve by tight fit, and the inner peripheral surface of the driven pulley is fixed. The surface is formed as a single cylindrical surface over the entire length in the axial direction, and each of the bearing outer rings is fitted inside both ends of the inner peripheral surface of the driven pulley. Of these, the end faces of the driven pulley opposite to the one-way clutch are held down by caulking portions formed in such a manner as to project inward in the diametrical direction at the inner peripheral edges of both end faces in the axial direction of the driven pulley.

[0016]

In the pulley device with a built-in one-way clutch for an alternator according to the present invention constructed as described above, the outer ring for each bearing has a clearance fit or a small interference with both ends of the inner peripheral surface of the driven pulley. The axial position of each of the bearing outer rings can be restricted even if the inner ring is fitted by interference fit. Therefore, the dispersion of the radial internal gap of each support bearing after assembling is reduced, and this internal clearance is set to an appropriate value, or a difference between the internal gaps of both support bearings is prevented. it can. Therefore, when the one-way clutch is locked, the driven pulley swings or the durability of each of the support bearings is impaired, or the rolling surfaces of a plurality of lock members constituting the one-way clutch are opposed to each other. It is possible to prevent a problem such as one-sided contact with the side peripheral surface. Furthermore, when the one-way clutch is locked, the contact position in the circumferential direction between the rolling surface of each lock member and the peripheral surface of the other party can be restricted to a target position (regular position). For this reason, the inconvenience that the locked state of the one-way clutch becomes uncertain can be prevented.

In particular, in the case of the present invention, of the axial outer end surfaces of the respective bearing outer races, the end surface opposite to the one-way clutch is formed at the inner peripheral edge portion of the driven axial end surface of each driven pulley. It is suppressed by the swaged part. Therefore, even if a step surface is not formed on the inner peripheral surface of the driven pulley, it is possible to prevent the driven pulley from moving in the axial direction with respect to the sleeve. Therefore, in the case of the present invention, the inner peripheral surface of the driven pulley can be formed into a single cylindrical surface over the entire length in the axial direction, and the processing cost of the driven pulley can be reduced.

[0018]

1 and 2 show a first embodiment of the present invention. The pulley device with a built-in one-way clutch for an alternator according to the present embodiment includes a rotating shaft 3 of the alternator 1.
(Refer to FIG. 5).
A driven pulley 7b is arranged around the sleeve 8a concentrically with the sleeve 8a. A one-way clutch 9a and a pair of support bearings 10 are provided between the inner peripheral surface of the driven pulley 7b and the outer peripheral surface of the sleeve 8a.
10 are provided.

The sleeve 8a is formed in a cylindrical shape as a whole. The sleeve 8a is externally fitted and fixed to the end of the rotating shaft 3 of the alternator 1, and is rotatable together with the rotating shaft 3. For this purpose, in the illustrated example, a screw hole 24 is formed in the middle of the inner peripheral surface of the sleeve 8a, and the screw hole 24 and the rotating shaft 3 are formed.
And a male screw portion provided on the outer peripheral surface of the tip portion. A locking hole 25 having a hexagonal cross section is formed at the tip of the inner peripheral surface (left end in FIG. 1) of the sleeve 8a, and a tool such as a hexagon wrench is formed in the locking hole 25. Can be freely locked at the tip. Further, a base end (the right end in FIG. 1) of the inner peripheral surface of the sleeve 8a is a circular hole 26 which can be freely fitted to the middle portion of the rotary shaft 3 near the front end. Incidentally, the structure in which the sleeve 8a and the rotating shaft 3 are combined so as not to rotate relative to each other may employ other structures such as spline engagement, non-circular engagement, and key engagement. Further, on the outer peripheral surface of such a sleeve 8a, a convex portion 27 projecting diametrically outward from the outer peripheral surface is formed over the entire periphery.

On the other hand, the first half of the outer peripheral surface of the driven pulley 7b (the left half in FIG. 1) has a cross-sectional shape extending in the width direction, so that a part of the endless belt 32 (FIG. 6) can be freely passed. I have. In particular, in the case of this example, the inner peripheral surface of the driven pulley 7b is formed in a single cylindrical shape over the entire length in the axial direction, except for a chamfered portion formed at the peripheral edge of the opening at both ends. And
The one-way clutch 9a is provided at an axially intermediate portion of a space existing between the outer peripheral surface of the sleeve 8a and the inner peripheral surface of the driven pulley 7b. The support bearings 10 and 10 are arranged at positions sandwiching the support bearings from both sides in the axial direction.

The one-way clutch 9a transmits the torque between the driven pulley 7b and the sleeve 8a only when the driven pulley 7b tends to rotate relative to the sleeve 8a in a predetermined direction. To be free. In the illustrated example, a roller clutch is used as the one-way clutch 9a. Also, such a one-way clutch 9a
To this end, the clutch inner ring 11a is externally fixed to the convex portion 27 formed on the outer peripheral surface of the sleeve 8a by interference fit. The clutch inner race 11a is formed into a cylindrical shape by subjecting a steel plate such as carburized steel to plastic working such as press working, and has a cam surface 13 formed on an outer peripheral surface. That is, a plurality of recesses 12, called ramps, are formed on the outer peripheral surface of the clutch inner ring 11 a at equal intervals in the circumferential direction, so that the outer peripheral surface is the cam surface 13.

On the other hand, of the inner peripheral surface of the clutch outer ring 28, which is internally fixed to the inner peripheral surface of the intermediate portion of the driven pulley 7b by interference fit, at least the roller 1 described below.
The axially intermediate portion that comes into contact with 6, 16 is simply a cylindrical surface. Such an outer ring 28 for a clutch is also formed entirely into a cylindrical shape by subjecting a steel plate of carburized steel or the like to plastic working such as press working, and has flanges 29a and 29b having inward flanges at both ends in the axial direction. Has formed. In addition, these both collar parts 2
9a, 29b, one (left side in FIG. 1) flange 29a
Is formed in advance at the time of manufacture of the clutch outer ring 28, so that it has the same thickness as the cylindrical portion of the clutch outer ring 28. In contrast, the other (right side in FIG. 1) flange 2
9b is made thin by incorporating rollers 16 and 16 and a retainer 17a for a clutch, which will be described below, inside the outer race 28 for a clutch in the diameter direction.

The plurality of rollers 16, 16, which constitute the one-way clutch 9a together with the clutch inner race 11a and the clutch outer race 28, cannot rotate the clutch inner race 11a with respect to the clutch inner race 11a. A synthetic resin clutch retainer 17a externally fitted as
In addition, it is supported so as to be freely displaceable in the rolling and circumferential directions. A spring such as a leaf spring or a synthetic resin spring integrated with the clutch retainer 17a is provided between the column provided on the clutch retainer 17a and the rollers 16, 16. The rollers 16, 16 are elastically pressed in the same direction with respect to the circumferential direction. Further, in the state shown in the drawing, the outer diameter side portions of both axial end surfaces of the clutch retainer 17a are the two flange portions 2 constituting the clutch outer race 28.
The clutch retainer 17a is prevented from being displaced in the axial direction by closely opposing the inner surfaces of 9a and 29b.
Since the basic structure and operation of such a one-way clutch 9a are well known in the related art, further detailed illustration and description will be omitted.

The support bearings 10, 10 allow the driven pulley 7b and the sleeve 8a to rotate relative to each other while supporting the radial load applied to the driven pulley 7b. Also in the case of this example, each such support bearing 1
As 0 and 10, a deep groove type ball bearing is used as in the case of the conventional structure shown in FIG. That is, each of these support bearings 10, 10 has a bearing inner ring 19, 19 having a deep groove type inner ring raceway 18, 18 on its outer peripheral surface.
A bearing outer ring 21, 21 having a deep groove type outer ring track 20, 20 on each inner peripheral surface;
A plurality of balls 22, 22 are provided between the outer ring raceway 8 and the outer raceways 20, 20 so as to be freely rolled. In the case of this example, each of the bearing inner rings 19, 19 is connected to the sleeve 8
a and externally fixed to both ends of the outer peripheral surface by a tight fit having a sufficient interference,
Are fixed to both ends of the inner peripheral surface of the driven pulley 7b by an interference fit having a small interference.

More specifically, the interference of the fitting portion between the sleeve 8a and the bearing inner rings 19 is set to 15 to 40 μm.
The value is set to a large value of about m to prevent the occurrence of creep (slipping) at each of these fitting portions. In the case of this example, the bearing inner rings 19, 19 are press-fitted into the outer peripheral surface of the sleeve 8a so that the bearing inner rings 19, 19 are externally fixed to the outer peripheral surface of the sleeve 8a by interference fit. When
To prevent these bearing inner rings 19, 19 from galling on the outer peripheral surface of the sleeve 8a, the sleeve 8a is
It is made of a material having a hardness of about 300 to 400 in S45C or the like. On the other hand, the interference of the fitting portion between the driven pulley 7b and the outer races 21 for bearings is 1 to 30 μm.
m, and these fitting portions are loosely fitted. In the case of this example, the reason why the fitting between the driven pulley 7b and the bearing outer rings 21 and 21 is not a gap fitting is that each of the balls 22, 22 and the one-way clutch 9a described below through these fitting portions. This is to prevent the lubricating grease sealed in the space in which is installed from leaking to the outside.
However, if there is no need to consider the prevention of grease leakage at the fitting surface, the driven pulley 7b and the bearing outer races 21,
The fitting with 21 can be a gap fitting.

A plurality of (for example, four) circumferential portions of the inner peripheral edge portions of both end faces of the driven pulley 7b are plastically deformed by a tool such as a caulking blade or a punch to form the caulked portion 3.
The outer end faces (the end faces on the opposite side of the one-way clutch 9a) of the bearing outer races 21, 21 are suppressed by the caulked portions 30, 30. Accordingly, even when a thrust load is applied to the driven pulley 7b, the driven pulley 7b is prevented from moving in the axial direction with respect to the sleeve 8a. The caulking portions 30, 30 as described above can also be formed by plastically deforming the inner peripheral edge portion over the entire circumference. In the case of the example shown in the figure, each ball 2 constituting each of the support bearings 10 and 10 is used.
Only the opening on the opposite side of the one-way clutch 9a is closed by the seal rings 31, 31 in the space in which the two-way clutch 22 is installed. This allows the space in which the balls 22 and 22 are installed to communicate with the space in which the one-way clutch 9a is installed so that the lubricating grease sealed in these spaces can be shared.

In the case of the pulley device with a built-in one-way clutch for an alternator of the present embodiment constructed as described above, the outer races 21 for the bearings are respectively provided with a small interference with both ends of the inner peripheral surface of the driven pulley 7b. The inner fit is fixed by a tight fit with For this reason, the dispersion of the radial internal gaps of the support bearings 10 and 10 after assembling is reduced, and the internal gaps are adjusted to an appropriate value. A difference can be prevented. For this reason, the one-way clutch 9
When the driven pulley 7b swings or the durability of the support bearings 10 and 10 is impaired at the time of locking the lock a, the rolling surfaces of the rollers 16 and 16 constituting the one-way clutch 9a may be inconsistent. Therefore, it is possible to prevent a problem such as a one-sided contact with the cam surface 13 and the inner peripheral surface of the clutch outer ring 28. Further, when the one-way clutch 9a is locked, the contact position in the circumferential direction between the rolling surface of each of the rollers 16, 16 and the cam surface 13 and the inner peripheral surface of the clutch outer ring 28 is set to a target position. (Regular position). For this reason, the inconvenience that the locked state of the one-way clutch 9a becomes uncertain can be prevented.

In particular, in the case of the present invention, the outer end faces of the bearing outer races 21 are respectively connected to the driven pulleys 7b.
Are held down by caulking portions 30 formed on the inner peripheral edge portions of both end faces. Therefore, even if a step surface is not formed on the inner peripheral surface of the driven pulley 7b, the driven pulley 7b can be prevented from moving in the axial direction with respect to the sleeve 8a. Therefore, the inner peripheral surface of the driven pulley 7b can be formed as a single cylindrical surface over the entire length in the axial direction, and the processing cost of the driven pulley 7b can be reduced. As a result, the manufacturing cost of the one-way clutch built-in pulley device for the alternator can be reduced.

FIG. 3 shows a second embodiment of the present invention.
An example is shown. In the case of this example, the width dimension (axial dimension) of the convex portion 27a formed on the outer peripheral surface of the sleeve 8a is increased, and the inner ring 1 for each bearing is provided on both axial end surfaces of the convex portion 27a.
The inner end faces 9 and 19 are abutted. This makes it possible to more reliably prevent the driven pulley 7b from moving in the axial direction with respect to the sleeve 8a. Other configurations and operations are the same as those of the above-described first example.

Next, FIG. 4 shows a third embodiment of the present invention.
An example is shown. In the case of this example, the formation of the convex portion on the outer peripheral surface of the sleeve 8b is omitted, and the outer peripheral surface of the sleeve 8b is simply formed over the entire length in the axial direction except for the chamfered portions formed at both axial edges. It has a cylindrical shape. Thereby, the processing cost of the sleeve 8b is reduced. In the case of this example, seal rings 31, 31 are also attached to the openings on the one-way clutch 9a side in the spaces in which the balls 22, 22, which constitute the support bearings 10, 10, are installed. This separates the space in which the balls 22 and 22 that do not require much grease are installed from the space in which the one-way clutch 9a that requires a lot of grease is installed. The amount of grease can be filled freely. Other configurations and operations are the same as in the case of the above-described first example.

In each of the above-described examples, the case where the low clutch is used as the one-way clutch has been described. However, the present invention has conventionally known the one-way clutch such as a cam clutch such as a sprag clutch. The same effect can be obtained even when a one-way clutch having another structure is used. Further, the pair of support bearings is not limited to the case where one pair of ball bearings is used, and the same applies to the case where one pair of roller bearings or ball bearings is used. The effect of is obtained.

[0032]

The pulley device with a built-in one-way clutch for an alternator according to the present invention is constructed and operates as described above, so that it is possible not only to prevent problems from occurring during operation, but also to reduce manufacturing costs.

[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 view as seen from an arrow A in FIG. 1;

FIG. 3 is a sectional view showing a second example of the embodiment of the present invention.

FIG. 4 is a sectional view showing the third example.

FIG. 5 is a sectional view showing an example of a conventionally known alternator.

FIG. 6 is a half sectional view showing one example of a conventional structure.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 alternator 2 housing 3 rotating shaft 4 rolling bearing 5 rotor 6 commutator 7, 7a, 7b driven pulley 8, 8a, 8b sleeve 9, 9a one-way clutch 10 support bearing 11, 11a inner ring for clutch 12 recess 13 cam surface 14th Second sleeve 15 Cylindrical surface 16 Roller 17, 17a Clutch retainer 18 Inner ring raceway 19 Bearing inner ring 20 Outer ring raceway 21 Bearing outer ring 22 Ball 23 Stepped surface 24 Screw hole 25 Lock hole 26 Circular hole 27 Projection 28 Outer ring for clutch 29a, 29b Flange part 30 Caulking part 31 Seal ring 32 Endless belt

Claims (1)

[Claims] 1. A sleeve which can be externally fitted and fixed to a rotating shaft of an alternator, a driven pulley disposed around the sleeve and concentric with the sleeve, an axially intermediate portion of an outer peripheral surface of the sleeve, and an inner periphery of the driven pulley. Provided between the driven pulley and the sleeve only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction. A one-way clutch, provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley at a position sandwiching the one-way clutch from both sides in the axial direction, and supporting the radial load applied to the driven pulley with these sleeves. A pair of support bearings, each of which is rotatable relative to a driven pulley, wherein each of the support bearings has an outer raceway on an inner peripheral surface thereof and is fitted in an inner peripheral surface of the driven pulley. An outer race for bearing, an inner raceway on the outer peripheral surface, an inner race for bearing fitted on the outer peripheral surface of the sleeve, and a plurality of rolling members rotatably provided between the outer raceway and the inner raceway. In a pulley device with a built-in one-way clutch for an alternator comprising a moving body, the inner races for bearings are externally fitted and fixed to both ends of the outer peripheral surface of the sleeve by interference fit, and the inner peripheral surface of the driven pulley is fixed. A single cylindrical surface is formed over the entire length in the axial direction, and each of the outer rings for bearing is fitted inside both ends of the inner peripheral surface of the driven pulley. Characterized in that the end faces of the driven pulley opposite to the one-way clutch are pressed to the inner peripheral edges of both end faces in the axial direction of the driven pulley by staking portions formed in a state of being diametrically inward. Built-in one-way clutch Pulley apparatus.