JP2000227151A - One-way clutch-incorporated pulley device for alternator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the axial shifting of a holder constituting a one-way clutch by eliminating the causes of cost increases, for example dispensing with burdensome machining. SOLUTION: The outer diameters D16 of the inner rings 16 and 16 of support bearings 9a and 9a provided in both sides of a one-way clutch 10a are set larger than the inner diameter R21 of a holder 21. By engagement between a portion near the axial both end surface of the holder 21 and the axial both ends of the inner rings 16 and 16, the axial shifting of the holder 21 is prevented.

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 for an alternator, which is fixed to an end of a rotating shaft of an alternator as a generator for an automobile and fixed to an end of a crankshaft of an engine. It is used to drive the alternator by passing an endless belt between the pulleys.

[0002]

2. Description of the Related Art The structure of an alternator for generating electric power necessary for an automobile by 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
Nos. 17807 and 8-61443, Tokuhei 7
No. 72585, French Patent Publication FR 27260
59A1 and the like describe a pulley device with a built-in one-way clutch for an alternator having the above-described functions.
In addition, such a pulley device with a built-in one-way clutch for an alternator is actually used.

FIG. 6 shows a pulley device with a built-in one-way clutch for an alternator described in Japanese Patent Application Laid-Open No. Hei 8-61443. This one-way clutch built-in pulley device for an alternator has a sleeve 8 that can be externally fitted and fixed to the rotating shaft 3. And this sleeve 8
And a driven pulley 7a is arranged concentrically with the sleeve 8. A pair of support bearings 9 is provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a.
9 and a one-way clutch 10 are provided. 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.
The rotation relative to a can be freely performed. Only when the driven pulley 7a tends to rotate relative to the sleeve 8 in a predetermined direction, the one-way clutch 10 can freely transmit the rotational force from the driven pulley 7a to the sleeve 8. .

The reason for using such a pulley device with a built-in one-way clutch for an alternator 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 11 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 (FIG. 5) driven to rotate by the endless belt 11 via the driven pulley 7 a includes the rotating shaft 3, the rotor 5 fixed to the rotating shaft 3, and the commutator 6 (FIG. 5). ) Does not fluctuate so rapidly. Therefore, when the driven pulley 7a is simply fixed to the rotating shaft 3, the endless belt 11 and the driven pulley 7a tend to rub in both directions with a change in the rotational angular speed of the crankshaft. As a result, the endless belt 11 rubbing against the driven pulley 7a
Stresses in different directions are repeatedly applied to cause slippage between the endless belt 11 and the driven pulley 7a, or shorten the life of the endless belt 11.

The endless belt 1 based on the friction between the outer peripheral surface of the driven pulley 7a and the inner peripheral surface of the endless belt 11 as described above.
The reduction in the service life of 1 also occurs by repeating acceleration and deceleration during traveling. That is, the driving force is transmitted from the endless belt 11 side to the driven pulley 7a side during acceleration, while the driven pulley 7a that continues to rotate based on inertia as described above during deceleration is transmitted from the endless belt 11 to the driven pulley 7a side. A braking force acts. The braking force and the driving force are the same as those of the endless belt 11.
Acts as a friction force in the opposite direction to the inner peripheral surface of
Again, this causes a reduction in the life of the endless belt 11. In particular, 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 friction applied to the inner peripheral surface of the endless belt 11 based on the braking force As a result of an increase in force, the above-mentioned life is significantly reduced.

Therefore, by using the pulley device with a built-in one-way clutch for the alternator as the driven pulley 7a as described above, if the running speed of the endless belt 11 is constant or tends to increase, the driven The transmission of the rotational force from the pulley 7a to the rotary shaft 3 is made freely, and conversely, when the running speed of the endless belt 11 tends to decrease, the relative rotation between the driven pulley 7a and the rotary shaft 3 becomes free. . That is, when the running speed of the endless belt 11 tends to decrease, the rotational angular speed of the driven pulley 7a is made slower than the rotational angular speed of the rotary shaft 3 so that the contact between the endless belt 11 and the driven pulley 7a is reduced. Prevents the contact parts from rubbing strongly. In this manner, the direction of the stress acting on the rubbed portion between the driven pulley 7a and the endless belt 11 is made constant, and slippage occurs between the endless belt 11 and the driven pulley 7a, or 11 is prevented from being shortened.

When the pulley apparatus with a built-in one-way clutch for an alternator as described above is constructed, the one-way clutch is a sprag-type one-way clutch that uses a sprag as a plurality of locking members, all of which are conventionally known. A clutch or a roller clutch using rollers as a plurality of locking members is used. Any one-way clutch requires a retainer for retaining the lock member.
When such a one-way clutch is incorporated in a pulley device with a built-in one-way clutch for an alternator, it is necessary to prevent the retainer from moving in the axial direction.
For this reason, conventionally, as described in JP-A-7-317807, an engaging portion is provided between a pulley incorporating a one-way clutch and a retainer to prevent the retainer from moving in the axial direction. The thing was being considered.

[0009]

In order to prevent the retainer from moving in the axial direction, it is troublesome to provide an engaging portion between the pulley and the retainer, and the cost of the one-way clutch built-in pulley device for the alternator is reduced. It will cause it to be higher. In view of such circumstances, the present invention has a built-in one-way clutch for an alternator, which can prevent a cage constituting a one-way clutch from being displaced in an axial direction without performing extra processing on a pulley or a cage. It has been invented to realize a pulley device.

[0010]

A pulley device with a built-in one-way clutch for an alternator according to the present invention is, similarly to a conventionally known pulley device with a built-in one-way clutch for an alternator, externally fixed to a rotating shaft of the alternator. A free sleeve, a driven pulley disposed concentrically with the sleeve around the sleeve, and provided between an axial intermediate portion of an outer peripheral surface of the sleeve and an axial intermediate portion of an inner peripheral surface of the driven pulley; A one-way clutch that enables the 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; In the state of sandwiching,
A support bearing is provided between an outer peripheral surface of the sleeve and an inner peripheral surface of the driven pulley, and supports a radial load applied to the driven pulley and enables relative rotation between the sleeve and the driven pulley.

In particular, in the pulley device with a built-in one-way clutch for an alternator according to the present invention, the one-way clutch includes a plurality of lock members and a retainer for holding each of the lock members. . Further, each of the support bearings is provided with a plurality of rolls rotatably provided between an outer ring separate from the driven pulley, an inner ring separate from the sleeve, and an inner peripheral surface of the outer ring and an outer peripheral surface of the inner ring. And a plurality of rolling elements. The retainer of the one-way clutch constitutes at least one of the support bearings and is fitted and fixed to a member having a fitting surface having substantially the same diameter over the entire length in the axial direction. Alternatively, displacement in the axial direction is prevented by the inner ring.

[0012]

In the pulley device with a built-in one-way clutch for an alternator according to the present invention, the retainer forming the one-way clutch is displaced in the axial direction by the outer ring or the inner ring forming the support bearing. Prevent things. Therefore, it is not necessary to perform troublesome processing on the raceway made of hard metal, which constitutes the one-way clutch, and the cost of the pulley device with a built-in one-way clutch for an alternator can be reduced.

[0013]

FIG. 1 shows a first embodiment of the present invention. The sleeve 8 is formed in a cylindrical shape as a whole, is externally fitted and fixed to an end of a rotating shaft 3 (see FIGS. 5 to 6) of the alternator, and is rotatable together with the rotating shaft 3. For this reason, in the illustrated example, a female spline portion 12 is formed on the inner peripheral surface of the intermediate portion of the sleeve 8, and a male spline portion (not shown) formed on the outer peripheral surface of the female spline portion 12 and the end of the rotating shaft 3. And are freely engageable. The structure for preventing the relative rotation between the rotating shaft 3 and the sleeve 8 may be replaced by a screw, a fitting of non-cylindrical surfaces, a key engagement, or the like instead of the spline.

A driven pulley 7b is arranged concentrically with the sleeve 8 around the sleeve 8 as described above. The driven pulley 7b has a support bearing 9 described below inside thereof.
a, 9a and a sprag type one-way clutch 10a. Further, the outer peripheral surface of the driven pulley 7b has a cross-sectional shape extending in the width direction as a waveform, so that a part of an endless belt called a poly-V belt can be passed around.

A pair of support bearings 9a, 9a and one one-way clutch are provided between the outer peripheral surface of the sleeve 8 constructed as described above and the inner peripheral surface of the driven pulley 7b constructed as described above. 10a. Among these, the support bearings 9a, 9a allow the relative rotation between the sleeve 8 and the driven pulley 7b while supporting the radial load applied to the driven pulley 7b. In the illustrated example, a deep groove ball bearing is used as each of the support bearings 9a, 9a.
That is, each of these support bearings 9a and 9b has an outer ring 14 having a deep groove type outer ring raceway 13 on its inner peripheral surface.
14 and a deep groove type inner raceway 15, 1
5 and the outer raceways 13, 13
And rolling elements (balls) 17, 17, each of which is provided so as to be freely rolled by a plurality of pieces between the inner ring raceways 15, 15. Each of such support bearings 9a, 9a
The inner ring 16 and the outer ring 16 are fixed to the outer peripheral surface of the sleeve 8 by external fitting and fixed to the inner peripheral surface of the driven pulley 7b. It is provided between both ends of the outer peripheral surface of the sleeve 8 and both ends of the inner peripheral surface of the driven pulley 7b.

The one-way clutch 10a transmits the rotational force between the driven pulley 7b and the sleeve 8 only when the driven pulley 7b tends to rotate in a predetermined direction with respect to the sleeve 8. Be free. In order to constitute such a one-way clutch 10a, the one-way clutch inner ring 18 is externally fixed to the outer peripheral surface of the intermediate portion of the sleeve 8 by interference fitting. This one-way clutch inner race 18 is
The entire body is formed of a hard metal such as bearing steel into a cylindrical shape, and the inner and outer peripheral surfaces are respectively cylindrical surfaces. An outer ring 19 for a one-way clutch is fixedly fitted to the inner peripheral surface of the intermediate portion of the driven pulley 7b by interference fit. The outer ring 19 for the one-way clutch is also formed entirely of a hard metal such as bearing steel into a cylindrical shape, and the inner and outer peripheral surfaces are respectively cylindrical surfaces. A lock member is provided between the outer peripheral surface of the one-way clutch inner race 18 and the outer peripheral surface of the one-way clutch outer race 19.
A plurality of non-circular sprags 20 are provided while being held by a holder 21. In the case of this example, this cage 21
Is formed by subjecting a metal plate such as a steel plate to plastic working such as press working.

An elastic material such as a spring is provided between the retainer 21 and each sprag 20, and the sprags 20 are separated from the outer peripheral surface of the one-way clutch inner race 18 by the elastic material. The elasticity in the direction of pressing against the outer peripheral surface of the outer ring 19 is provided. Each of the sprags 20 is
When the one-way clutch inner race 18 and the one-way clutch outer race 19 rotate relative to each other in a predetermined direction, the outer peripheral surface of the one-way clutch inner race 18 and the inner peripheral surface of the one-way clutch outer race 19 are rotated. The one-way clutch inner race 18 and the one-way clutch outer race 19 transmit torque. On the other hand, when the one-way clutch inner race 18 and the one-way clutch outer race 19 relatively rotate in opposite directions, the sprags 20 separate the outer peripheral surface of the one-way clutch inner race 18 from the one-way clutch. The one-way clutch inner ring 18 and the one-way clutch outer ring 19 do not transmit torque due to sliding with respect to the inner peripheral surface of the outer ring 19 for use. The structure and operation of such a sprag-type one-way clutch 10a are well known in the related art, and a detailed description thereof will be omitted. The sprags 20 may have various shapes depending on the magnitude of torque to be transmitted and the like.

Furthermore, in the case of the built-in one-way clutch pulley apparatus for an alternator of the present invention, the outer diameter D ₁₈ of the one-way clutch inner race 18, wherein each support bearings 9a, 9
is smaller (D ₁₈ <D ₁₆₎ than the outer diameter D ₁₆ of the inner ring 16, 16 constituting the a. Accordingly, the outer peripheral surface of the one-way clutch inner ring 18 is supported by the support bearings 9a, 9a.
Are recessed inward in the diametrical direction from the outer peripheral surfaces of the inner rings 16, 16. The one-way clutch 10a
The inner diameter R ₂₁ of the cage 21 constituting the larger than the outer diameter D ₁₈ of the one-way clutch inner race 18 is smaller than the outer diameter D ₁₆ of the inner ring 16, 16 constituting the support bearings 9a, the 9a said (D ₁₈ <R ₂₁ <D ₁₆ ). Therefore, the ends of the retainer 21 near the inner diameter on both axial sides are opposed to the axial end faces of the inner rings 16, 16.
Therefore, the retainer 21 is prevented from being displaced in the axial direction (the left-right direction in FIG. 1) by the inner rings 16, 16. Therefore, the sprags 20 held by the retainer 21 do not come off the outer peripheral surface of the one-way clutch inner race 18 and the outer peripheral surface of the one-way clutch outer race 19.

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 rotation speed of the driven pulley 7b over which the endless belt is stretched is controlled by the function of the one-way clutch 10a. Only when the rotation speed of the sleeve 8 fixed to the rotating shaft of the alternator is higher than that, the torque is transmitted from the driven pulley 7 to the rotating shaft. Conversely, when the rotation speed of the driven pulley 7b is lower than the rotation speed of the sleeve 8, the connection between the driven pulley 7b and the sleeve 8 is cut off to prevent an excessive force from being applied to the endless belt. I do. In particular, in the case of the pulley device with a built-in one-way clutch for an alternator of the present embodiment, the inner races 16, 16 constituting the support bearings 9a, 9a described above.
This prevents the cage 21 constituting the one-way clutch 10a from being displaced in the axial direction. Therefore, it is not necessary to perform troublesome processing on the one-way clutch inner ring 18 and the one-way clutch outer ring 19, each of which is made of hard metal such as bearing steel, which constitutes the one-way clutch 10a. The cost of the built-in pulley device can be reduced.

In the illustrated example, the outer diameter D ₂₁ of the retainer 21 is made smaller (D ₂₁ <R ₁₄ ) than the inner diameter R _{14 of the} outer races 14, 14 constituting the support bearings 9 a, 9 a. ing. Therefore, the inner ring 1 that constitutes one of the support bearings 9a has an end near the inner diameter on one side surface in the axial direction of the retainer 21.
Even when the cage 21 abuts on the end face, the end of the retainer 21 near the outer diameter on one side in the axial direction does not contact the end face of the outer ring 14 constituting any of the support bearings 9a. Therefore, the retainer 21 does not rub against the outer ring 14 and the inner ring 16 that rotate relative to each other so that the rotational resistance of the support bearing 9a does not increase.

As a modification of the present embodiment, the above-mentioned cage 21
The outer diameter and the inner diameter of the retainer 21 are made larger than those in the illustrated example, and the axially opposite end faces of the retainer 21 and the outer races 14, 14 constituting the support bearings 9a, 9a are formed. The engagement can also prevent the displacement of the retainer 21 in the axial direction. Further, the retainer 21 does not necessarily need to be engaged with the axial end surfaces of the outer rings 14 and 14 or the inner rings 16 and 16 constituting the support bearings 9a and 9a over the entire circumference. Part of the circumference is projected in the diameter direction,
This protruding part is connected to the outer ring 14, 14 or the inner ring 1
6, 16 may be engaged with the axial end surfaces.

In any case, like the pulley device with a built-in one-way clutch for an alternator according to the present invention, the axial displacement of the retainer 21 constituting the one-way clutch 10a is controlled by the outer ring 14, 14 or the inner ring. If the outer ring 1 is configured to be blocked based on engagement with the axial end surfaces of the outer races 1 and 16,
The inner peripheral surface of the driven pulley 7b or the outer peripheral surface of the sleeve 8 which is a fitting surface for fitting and fixing the inner rings 4, 14 or the inner rings 16, 16 has substantially the same diameter dimension (inner diameter or inner diameter) over the entire axial length. Is the outer diameter) of the driven pulley 7b or the sleeve 8
Can be easily processed and cost can be reduced. In the illustrated example, the inner peripheral surface of the driven pulley 7b and the sleeve 8
Are formed as cylindrical surfaces having substantially the same diameter over the entire axial length. However, each of the above support bearings 9
Depending on the magnitude of the basic dynamic load rating required for the a and 9a and the value of the torque capacity required for the one-way clutch 10a, the two peripheral surfaces are formed into cylindrical surfaces having substantially the same diameter over the entire axial length. It may not be possible. In such a case, only one of the peripheral surfaces is formed into such a cylindrical surface, and the raceway (the outer ring 14, 14 or the inner ring 1) fitted and fixed to the peripheral surface is used.
6, 16), the cage 21 is prevented from being displaced in the axial direction.

Next, FIG. 2 shows a second embodiment of the present invention.
An example is shown. In the case of this example, the one-way clutch 10
As b, a roller clutch is used. Therefore, in the case of this example, a plurality of recesses 24 called ramps are formed at equal intervals in the circumferential direction on the outer peripheral surface of the one-way clutch inner ring 18a constituting the one-way clutch 10b. A cam surface 22 is formed on the outer peripheral surface. On the other hand, the inner peripheral surface of the one-way clutch outer ring 19a is a simple cylindrical surface. In addition, these one-way clutch inner races 1
A plurality of rollers 23 each constituting a one-way clutch together with a one-way clutch 10b together with the one-way clutch 10b together with a one-way clutch 8a and a one-way clutch outer ring 19a are formed of a synthetic resin cage 21a
In addition, it is supported so as to be freely displaceable in the rolling and circumferential directions. An elastic material such as a spring is provided between the column provided on the retainer 21a and each of the rollers 23, and these rollers 23 are elastically pressed in the same direction with respect to the circumferential direction. . Since the structure and operation of the roller clutch are also well known in the related art, similarly to the sprag type one-way clutch, detailed illustration and description are omitted.

In the case of the present embodiment, projecting pieces 25, 25 are formed at both ends in the axial direction of the inner peripheral surface of the retainer 21a, at the portions corresponding to the respective recesses 24, and the projecting pieces 25, 25 are formed. Into the recesses 24 to prevent rotation of the retainer 21a with respect to the one-way clutch inner race 18a. The diameter D of the largest inscribed circle of each of these protruding pieces 25, 25
Reference numeral ₂₅ denotes an inner ring 1 constituting a pair of support bearings 9a, 9a.
The outer diameters D _{16 and} D ₁₆ are smaller (D ₂₅ <D ₁₆ ). Therefore, in the case of this example, the axial displacement of the retainer 21a is prevented by the engagement between the axial one side surface of each of the protruding pieces 25, 25 and the axial end surface of each of the inner rings 16, 16. are doing. For this reason, in the case of this example,
a of the one-way clutch inner race 18a and the inner peripheral surface of the one-way clutch outer race 19a.
It does not come off from the cam surface 22 formed on the outer peripheral surface of a.

In the illustrated example, both ends in the axial direction of the retainer 21a are positioned between the inner peripheral surfaces of the outer rings 14 and 14 and the outer peripheral surfaces of the inner rings 16 and 16 that constitute the support bearings 9a and 9a. In the space. The reason for this configuration is that the rims 2 provided at both ends in the axial direction of the retainer 21a are provided.
This is to secure the cross-sectional area of 6, 6 and the rigidity of the retainer 21a. In the case of this example, each of the protruding pieces 2
5 and 25 can be engaged with the recesses 24 by interference fit. However, even in this case, the protruding pieces 25 and 25
The diameter D ₂₅ of the maximum inscribed circle is smaller than the outer diameter D 16 of each of the inner races 16, ₁₆ , so that even when the engagement between each of the projections 25, 25 and each of the recesses 24 is loosened, Cage 21a
Must be prevented from being displaced in the axial direction. Other configurations and operations are the same as in the case of the above-described first example.

FIG. 3 shows a third embodiment of the present invention.
An example is shown. Also in the case of this example, the one-way clutch 10c
As a roller clutch. In particular, in the case of this example, the axial dimension of the one-way clutch inner race 18b constituting the one-way clutch 10c is set to the one-way clutch outer race 19a also constituting the one-way clutch 10c.
Is smaller than the dimension in the axial direction. One axial end surface of the one-way clutch inner race 18b (the right end surface in FIG. 3).
A gap 27 is interposed over the entire circumference between the support ring 9a and the one end (the right side in FIG. 3) of the inner ring 16 that constitutes the support bearing 9a. On the other hand, at one axial end of the inner peripheral surface of the retainer 21b that constitutes the one-way clutch 10c, an inward flange-shaped engaging flange 28 is continuously provided over the entire circumference.
Or it is formed intermittently. And, this engagement collar portion 28
Into the gap 27 loosely or press-fit. In the case of such an example, the engagement flange 28 and the gap 27
, The displacement of the retainer 21b in the axial direction is prevented, and each roller 2 held by the retainer 21b is prevented.
3 is prevented from coming off from the inner peripheral surface of the one-way clutch outer race 19a and the cam surface 22 formed on the outer peripheral surface of the one-way clutch inner race 18b.

In the illustrated example, the one-way clutch 1
A gap 27 is provided between one end in the axial direction of the inner race 18b constituting the one-way clutch 10c and one end of the inner race 18b constituting the one-way clutch 10c. It is also possible to provide a small-diameter portion in the portion, and abut the end surface of the small-diameter portion against the axial end surface of the inner ring 16 constituting the one support bearing 9a. In such a case, the engagement flange 28 is inserted into the outer diameter side of the small diameter portion. Other configurations and operations are the same as those of the above-described second example, and therefore, the description of the equivalent parts will be omitted.

FIG. 4 shows a fourth embodiment of the present invention.
An example is shown. In the case of this example, between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7b, a pair of support bearings 9b, 9b each being a radial roller bearing, and one A direction clutch 10d is provided. In order to constitute the one-way clutch 10d, the one-way clutch inner race 18c is externally fitted to the outer peripheral surface of the intermediate portion of the sleeve 8 by interference fitting. The one-way clutch inner race 18c is formed entirely of a hard metal plate such as bearing steel or a carburized steel plate such as SCM415 into a cylindrical shape, and the outer peripheral surface is a cam surface 22a.
In order to form the support bearings 9b, 9b, inner peripheral surfaces 16a,
16a is externally fixed by interference fit. Each of these inner rings 16a, 16 is made of a hard metal plate such as bearing steel or a carburized steel plate such as SCM415.
a is formed in a cylindrical shape with an L-shaped cross section by forming an inner ring side flange portion 29 having an outward flange shape at one end edge of the cylindrical portion 38.

Each of the inner races 16a, 16a is fitted to the sleeve 8 with the inner race side flanges 29 located on the opposite sides, and the leading edge of each inner race is formed on the one-way clutch inner race 18c. It abuts against both axial edges. In the case of this example, the outer diameter D _16a of the cylindrical portion of each of the inner rings 16a, 16a is set to the diameter D _{24 of the} inscribed circle with respect to the bottom of the plurality of recesses 24 formed on the outer peripheral surface of the one-way clutch inner ring 18c. (D _16a > D ₂₄ ). The retainer 21c that constitutes the one-way clutch 10d
Each protruding piece 2 formed on the inner peripheral surface of the
5a, 25a is attached to each of the inner rings 16a, 16
The retainer 21c is prevented from moving in the axial direction by facing the edge of “a”.

On the other hand, an outer ring 30 is internally fixed to the intermediate portion of the driven pulley 7b by interference fit. The outer ring 30 functions not only as an outer ring of the one-way clutch 10d but also as an outer ring of each of the support bearings 9b, 9b, and is also made of a hard metal plate such as bearing steel or carburized steel such as SCM415. The whole is formed into a cylindrical shape by, for example, pressing a plate material. Outer ring 3 like this
Outer ring side flange portions 31a and 31b each having an inward flange shape are formed on both end edges in the axial direction of 0. It should be noted that one of these outer ring side flange portions 31a and 31b (left side in FIG. 4) is formed before being combined with the other constituent members, so that the outer ring side flange portion 31a and the main body portion of the outer ring 30 are not formed. It has similar thickness dimensions. On the other hand, the other outer ring side flange portion 31b (right side in FIG. 4) is formed to be thin after being formed after being combined with other components.

The one-way clutch 10d includes an inner peripheral surface of an intermediate portion of the outer race 30 and an outer peripheral surface of the one-way clutch inner race 18c. That is, the inner peripheral surface of the intermediate portion of the outer race 30 and the inner race 18 for the one-way clutch
c, a cage 21 c formed of a synthetic resin in a cage shape cylindrical shape, and a plurality of rollers 23
And a spring (not shown). Also, the retainer 21c
As described above, each of the projecting pieces 2 formed on the inner peripheral surface thereof
5a and 25a are engaged with the concave portion 24 forming the cam surface 22a of the one-way clutch inner ring 18c to prevent relative rotation with respect to the one-way clutch inner ring 18c.

Each of the support bearings 9b, 9b includes the respective inner ring 16a, 16a and a portion near the axial end of the outer ring 30. That is, each of the inner rings 1
Cages 32, 32 each formed of a synthetic resin in a cage shape between the outer peripheral surfaces of 6 a, 16 a and the inner peripheral surfaces of the outer ring 30 near both ends in the axial direction;
A plurality of rollers 33 rotatably held by 2, 32;
33 are arranged to constitute a radial roller bearing.

Floating washers 34, 34 are provided between the outer surfaces of the outer ring side flanges 31a, 31b and the inner surfaces of the inner ring side flanges 29, 29, respectively. 31a, 31b and inner ring side flanges 29, 2
9 and freely mounted relative to it. Each of the above-mentioned floating washers 34 and 34 is made of a metal having self-lubricating properties such as copper, a metal which has been impregnated with a lubricating oil such as a tufftrided metal or an oil-impregnated metal, or a polyamide resin, a polyacetal resin or a polytetrafluoride. It is formed in a ring shape from a synthetic resin having a low friction coefficient such as an ethylene resin. Such floating washers 34, 34
Each of the outer ring side flanges 31a, 31b and the inner ring side flanges 29, 2
9 and loosely clamped. The floating washers 34, 34 guide (prevent radial displacement) the outer peripheral surfaces of the inner rings 16a, 16a or the inner peripheral surfaces of the driven pulleys 7b.

The gaps between the inner peripheral surfaces of the axial ends of the outer race 30 and the outer peripheral surfaces of the inner races 16a, 16a are closed by seal rings 35, 35, respectively. Each of these seal rings 35, 35 is constituted by a cored bar 36 and an elastic member 37, and is formed on the inner peripheral surface of both ends of the outer ring 30 in a state where the outer diameter of the elastic member 37 is elastically reduced. Supports internal fitting. Then, the leading edges of the plurality of seal lips provided on each of the elastic members 37, 37 are slidably contacted with the outer peripheral surfaces of the intermediate portions of the inner rings 16a, 16a and the inner surfaces of the outer ring side flange portions 31a, 31b. Abutting. In addition, the core metal 3 of each of the seal rings 35, 35 described above.
6, a portion facing the end face of the retainer 32 constituting each of the support bearings 9b, 9b is formed of the elastic material 37.
So that even if the end face of the retainer 32 and one side face of the cored bar 36 are in sliding contact with each other, the sliding resistance can be kept low. Also in the case of the structure of the present embodiment having such a configuration, the lock member 21c, which constitutes the one-way clutch 10d, can be prevented from being displaced in the axial direction without any particular troublesome processing or extra parts, and the locking member can be prevented. Can be prevented from coming off from the cam surface 22a formed on the outer peripheral surface of the one-way clutch inner ring 18c.

[0035]

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 a highly reliable structure can be realized without particularly increasing the cost.

[Brief description of the drawings]

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

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

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

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

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

FIG. 6 is a partial cross-sectional view showing one example of a conventional structure.

[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 Sleeve 9, 9a, 9b Support bearing 10, 10a, 10b, 10c, 10d One-way clutch 11 Endless belt 12 Female spline part Reference Signs List 13 outer ring track 14 outer ring 15 inner ring track 16, 16a inner ring 17 rolling element 18, 18a, 18b, 18c one-way clutch inner ring 19, 19a one-way clutch outer ring 20 sprags 21, 21a, 21b, 21c cage 22, 22a cam Surface 23 Roller 24 Concave part 25, 25a Projection piece 26 Rim part 27 Gap 28 Engagement flange part 29 Inner ring side flange part 30 Outer ring 31a, 31b Outer ring side flange part 32 Cage 33 Roller 34 Floating washer 35 Seal ring 36 Core metal 37 Elasticity Material 38 Cylindrical part

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. Between the driven pulley and the sleeve only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction. The one-way clutch is provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley in a state where the one-way clutch is sandwiched from both sides in the axial direction, and is driven by these sleeves while supporting the radial load applied to the driven pulley. In a pulley device with a built-in one-way clutch for an alternator having a support bearing capable of rotating relative to a pulley, the one-way clutch includes a plurality of locking members. And a retainer for holding these lock members. Each of the support bearings has an outer ring separate from the driven pulley, an inner ring separate from the sleeve, and inner peripheral surfaces of these outer rings. And a plurality of rolling elements rotatably provided between the outer ring and the outer peripheral surface of the inner ring.The retainer of the one-way clutch includes at least one of the support bearings. A one-way clutch for an alternator, wherein the axial displacement is prevented by an outer ring or an inner ring fitted and fixed to a member having a fitting surface having substantially the same diameter over the entire length in the axial direction. Built-in pulley device.