JP2002139133A - Rotation transmitter with built-in one-way clutch and method of assembling the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently secure the sealing performance of a seal ring 26 to be attached to a support bearing 10 regardless of the dimensional error of each member constituting the support bearing 10, and to provide a method of easily assembling the support bearing 10 for a rotation transmitter with a built-in one-way clutch. SOLUTION: An outer ring 22 supporting the seal ring 26 is forced into an objective surface 31 while shifting the outer ring 22 by a quantity equivalent to the dimension X in the axial direction from an inner ring 24 forming the objective surface 31. In this way, the tightening margin λ of the abutting part of the top end edge of a seal lip 30 constituting the seal ring 26 to the objective surface 31 can be sufficiently secured. The forcing work is carried out by pressing the end surfaces of the outer ring 22 and the inner ring 24 at the same time with a stepped presser surface formed at a part of a press-in jig.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved one-way clutch-equipped rotation transmission device which can be used as a driven pulley fixed to an end of a rotating shaft of an alternator, for example, a generator for an automobile. The present invention relates to a method for assembling a rotation transmission device with a built-in clutch.

[0002]

2. Description of the Related Art The structure of an alternator for generating electric power necessary for an automobile by using a driving engine of the automobile as a drive source is described in, for example, Japanese Patent Application Laid-Open No. 7-139550. FIG. 5 shows an alternator 1 described in this publication. A rotating shaft 3 is rotatably supported by a pair of rolling bearings 4 and 4 inside the housing 2. 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 wrapped around the driven pulley 7, and the rotary shaft 3 is rotatably driven by the crankshaft of the engine.

Conventionally, as the driven pulley 7, 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, power can be freely transmitted from the endless belt to the rotating shaft, and when the traveling speed of the endless belt tends to decrease, Various one-way clutch built-in pulley devices, which are built-in one-way clutch type rotation transmission devices that allow the relative rotation between the driven pulley and the rotary shaft, have been proposed and are used in part. For example, JP-A-56-10
1353, JP-A-7-317807, 8
JP-A-61443, JP-A-8-226462, JP-B-7-72585, French Patent Publication FR272
6059A1 and the like describe a pulley device with a built-in one-way clutch having the functions as described above.

FIGS. 6 and 7 show an example of a pulley device with a built-in one-way clutch which is conventionally known, for example, as described in these publications. This one-way clutch built-in pulley device includes a rotating shaft 3 of an alternator 1 (see FIG. 5).
And a sleeve 8 which is an inner diameter side member which can be externally fixed. A driven pulley 7 a, which is a cylindrical outer diameter side member, is arranged around the sleeve 8 concentrically with the sleeve 8. A roller clutch 9 which is a one-way clutch and a pair of support bearings 10 and 10 are provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a.

The sleeve 8 is formed in a cylindrical shape as a whole. The sleeve 8 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 11 is formed in the middle of the inner peripheral surface of the sleeve 8, and the screw hole 11 is screwed into a male screw portion provided on the outer peripheral surface of the tip of the rotary shaft 3. It is free.
The central portion of the outer peripheral surface of the sleeve 8 is a large-diameter portion 12 having a larger diameter than other portions.

[0006] On the other hand, the outer peripheral surface of the driven pulley 7a has a cross-sectional shape in the width direction in a waveform so that a part of an endless belt called a poly-V belt can be freely passed over. The roller clutch 9 is provided at an axially intermediate portion of the space existing between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a. The support bearings 10 and 10 are respectively arranged at positions where the support bearings are sandwiched from both sides in the axial direction.

Only when the driven pulley 7a tends to rotate relative to the sleeve 8 in a predetermined direction, the roller clutch 9 reduces the rotational force between the driven pulley 7a and the sleeve 8. Transmission is free. Such a roller clutch 9 includes a clutch inner ring 13, a clutch outer ring 14, a plurality of rollers 15, 15, a clutch retainer 16, and a spring (not shown). Of these, the clutch inner ring 13 is fitted and fixed to the outer peripheral surface of the large diameter portion 12 of the sleeve 8 and the clutch outer ring 14 is fitted to the inner peripheral surface of the intermediate portion of the driven pulley 7a by interference fitting. . In addition, at least an intermediate portion of the inner peripheral surface of the clutch outer ring 14 that comes into contact with the rollers 15 and 15 is a simple cylindrical surface, and an outer peripheral surface of the clutch inner ring 13 is a cam surface 17. That is, a plurality of recesses 18, 18, each called a ramp, are formed at equal intervals in the circumferential direction on the outer peripheral surface of the clutch inner ring 13, and the outer peripheral surface of the clutch inner ring 13 is And

Then, between the cam surface 17 and the inner peripheral surface of the clutch outer race 14, the plurality of rollers 15,
15 and the above-mentioned clutch retainer 16 that supports the rollers 15 and 15 so that they can roll and slightly displace in the circumferential direction. This clutch retainer 16
Is made entirely of synthetic resin (for example, synthetic resin such as polyamide 46 mixed with about 20% glass fiber), and its inner peripheral edge is engaged with a part of the cam surface 17 so that The rotation relative to the clutch inner ring 13 is prevented. At the same time, in the illustrated example, the convex portion 19 formed on the inner peripheral surface of the end portion of the clutch retainer 16 is
An outward flange-shaped flange portion 20 formed over the entire circumference at the end of the large diameter portion 12 of the sleeve 8 and the clutch inner race 13
Between the clutch retainer 16 and the clutch retainer 16.
Are positioned in the axial direction. Further, between the clutch retainer 16 and the rollers 15, 15, the rollers 15, 15 are pressed in the same direction with respect to the circumferential direction (the direction in which the recesses 18, 18 become shallower). , A spring (not shown) is provided.

When the above-described roller clutch 9 is constructed, the cylindrical surface and the cam surface 17 which come into contact with the plurality of rollers 15 are formed on the inner peripheral surface of the driven pulley 7a and the sleeve 8 respectively. It may be formed directly on the outer peripheral surface. The arrangement of the cylindrical surface and the cam surface 17 in the radial direction may be reversed from the above-described structure. In any case, since the structure and operation of such a roller clutch 9 are well known in the art, further detailed description will be omitted.

The pair of support bearings 10, 10
Supports the radial load applied to the driven pulley 7a from the endless belt to prevent the roller clutch 9 from being damaged. When the roller clutch 9 is overrun (unlocked), the driven pulley 7a The relative rotation with respect to the sleeve 8 is made free. In the illustrated example, a deep groove type ball bearing is used as each of the support bearings 10 and 10 as described above. That is, each of these support bearings 1
Reference numerals 0 and 10 respectively denote an outer ring 22 having a deep groove type outer raceway 21 on the inner peripheral surface, an inner race 24 having a deep groove type inner raceway 23 on the outer peripheral surface, and rolling between the outer raceway 21 and the inner raceway 23. It comprises a plurality of balls 25, 25 provided movably. Openings at both ends of the space in which the balls 25, 25 are located between the inner peripheral surface of the outer race 22 and the outer peripheral surface of the inner race 24 are sealed rings 26, 26, respectively.
It is closed by. This prevents the lubricant such as grease sealed in the space in which the balls 25, 25 are installed from leaking to the outside, and prevents foreign substances such as dust from entering the space. .

Each of the above-mentioned seal rings 26, 26 is formed by bending a steel plate made of SECC or the like, thereby forming a metal core 27 having an L-shaped cross section and a ring shape as a whole.
An elastic member 28 such as nitrile-butadiene rubber (NBR) reinforced by the metal core 27 forms an entire ring shape. As shown in detail in FIG. 7, each of the seal rings 26, 26 has a locking groove 2 formed by forming the outer peripheral edge of the elastic member 28 at both ends of the inner peripheral surface of the outer ring 22 over the entire circumference.
9 and 29, it is supported and fixed to the outer ring 22. The distal end edge of the seal lip 30 provided on the inner diameter side portion of the elastic member 28 is brought into contact with the mating surfaces 31 formed on the both ends of the inner ring 24 with an interference λ. . In the case of the illustrated example, each of these mating surfaces 3
Reference numerals 1 and 31 each denote an inclined surface facing the axial end edge of the inner ring 24, that is, an inclined surface inclined in such a direction that the outer diameter decreases toward the axial end of the inner ring 24.
In FIG. 7, the seal lip 30 is shown in a free state (a state in which the seal lip 30 is not elastically deformed along the mating surface 31).

Each of the support bearings 10 and 10 having the above-described seal rings 26 and 26 respectively connects the outer ring 22 and the inner ring 24 to the inner peripheral surfaces at both ends of the driven pulley 7a and both ends of the sleeve 8. Each is fitted and fixed to the outer peripheral surface by press fitting. In the case of the conventional one-way clutch built-in pulley device including the structure shown in FIGS. 6 and 7, the operation of press-fitting the outer ring 22 and the inner ring 24 to the inner and outer peripheral surfaces as described above is performed by using the outer ring 22 and the outer ring 22. The outer end face of the inner ring 24 {the end face on the side facing the outer space of the pulley device with a built-in one-way clutch (the side not facing the roller clutch 9)} is formed by a single plane provided on a part of the press-fitting jig. It is performed by pressing simultaneously. Therefore, the outer end faces of the outer ring 22 and the inner ring 24 are arranged on the same plane in a state where the press-fitting work of the outer ring 22 and the inner ring 24 is completed.

The seal ring 26 as described above is provided only at the opening on the side facing the external space of the pulley device with a built-in one-way clutch among the openings at both ends of the space where the balls 25, 25 are installed. In some cases, the space in which each of the balls 25, 25 is installed communicates with the space in which the roller clutch 9 is installed. When the two spaces are communicated in this way, the lubricant sealed in the communicated spaces can be shared by the support bearings 10 and 10 and the roller clutch 9.

There are two reasons for using the one-way clutch built-in type pulley device having the above-described configuration.
First, the first reason is to extend the life of the endless belt. For example, when the driving engine of the automobile is a diesel engine or a direct-injection gasoline engine, the rotation angular speed of the crankshaft greatly fluctuates during low rotation such as when idling. As a result, the running speed of the endless belt stretched over the drive pulley fixed to the end of the crankshaft also fluctuates finely. On the other hand, the rotation shaft 3 (FIG. 5) of the alternator 1 driven to rotate by the endless belt via a driven pulley is so sharply based on the inertia mass of the rotation shaft 3 and the rotor 5 fixed to the rotation shaft 3. Does not fluctuate. Therefore, when the driven pulley is simply fixed to the rotating shaft, the endless belt and the driven pulley tend to rub in both directions due to 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, so that slipping easily occurs between the endless belt and the driven pulley, or the life of the endless belt is shortened. Or cause.

Therefore, by using the one-way clutch built-in type pulley device as such a driven pulley,
When the running speed of the endless belt is constant or increasing, the transmission of the rotational force from the driven pulley to the rotating shaft 3 is enabled. On the contrary, when the running speed of the endless belt tends to decrease. Makes it possible to freely rotate the driven pulley and the rotating shaft 3 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 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 is strong. Prevent rubbing. In this way, the direction of the stress acting on the rubbed portion between the driven pulley and the endless belt is kept constant,
It prevents slippage between the endless belt and the driven pulley, or shortens the life of the endless belt.

The second reason is to improve the power generation efficiency of the alternator 1. The rotating shaft 3 to which the rotor 5 of the alternator 1 is fixed is rotationally driven by an automobile driving engine via an endless belt and a driven pulley. When a fixed driven pulley is used, when the rotation speed of the driving engine suddenly decreases, the rotor 5
Also rapidly decreases, and the amount of power generated by the alternator 1 also sharply decreases. On the other hand, if the pulley device with a built-in one-way clutch is used as a driven pulley attached to the alternator 1, the rotation speed of the rotor 5 can be reduced even if the rotation speed of the driving engine is rapidly reduced. It gradually decreases due to inertial force, and continues to generate power during that time. As a result, the power generation of the alternator 1 can be increased by effectively using the kinetic energy of the rotating shaft 3 and the rotor 5 as compared with the case where a fixed driven pulley is used.

[0017]

In the case of the conventional structure as described above, the support bearings 10, 10 are assembled to the pulley device with a built-in one-way clutch. Seal ring 26,
There is a possibility that the sealing performance of at least one of the seal rings 26 cannot be sufficiently secured. The reason will be described below.

In the case of the conventional structure described above, when the support bearings 10 and 10 are assembled to the pulley device with a built-in one-way clutch, as described above, the outer ring 22 and the inner ring 24 constituting these support bearings 10 and 10 are provided. Are arranged on the same plane. On the other hand, the outer ring 2
The dimensions of the respective parts of the inner ring 2 and the inner ring 24 (the width dimensions of the outer ring 22 and the inner ring 24, the formation positions of the locking groove 29 and the mating surface 31 in the axial direction, and the like) may have errors due to manufacturing. . Therefore, despite the existence of such errors,
If the outer end surfaces of the outer ring 22 and the inner ring 24 are always arranged on the same plane, the leading edge of the seal lip 30 forming each of the seal rings 26, 26 and the mating surface 31 are determined based on the existence of the error. May deviate from the appropriate range in the axial direction. Then, depending on the direction in which the positional relationship shifts, either one of the seal rings 2 may be used.
6 and the above-mentioned mating surface 3
As shown in FIG. 8, a relatively large interference between the contact edge of the seal lip 30 and the mating surface 31 is obtained. There may be gaps. When the interference of the contact portion between the leading edge of the seal lip 30 and the mating surface 31 is reduced or lost, the sealing performance of the seal ring 26 cannot be sufficiently ensured.

In this case, even if the sealing performance of the seal ring 26 on the side facing the roller clutch 9 cannot be ensured, the lubricant sealed in the space in which the balls 25, 25 are installed is filled with the one-way clutch type. There is no leakage to the external space of the pulley device. Further, as described above, the seal ring 26 on the side facing the roller clutch 9 omits the installation so that the space where the balls 25 and 25 are installed communicates with the space where the roller clutch 9 is installed. However, a lubricant may be shared between these two spaces. For this reason, if the type of the lubricant to be enclosed in these two spaces is the same, there is a particular problem even if the sealing performance of the seal ring 26 on the side facing the space where the roller clutch 9 is installed cannot be ensured. Nothing.

On the other hand, the seal ring 26 on the side opposed to the external space of the pulley device with a built-in one-way clutch.
When it becomes impossible to secure the sealing performance of
The lubricant sealed in the space in which 5 is installed leaks into the external space. As a result, the durability of each of the support bearings 10, 10 decreases. Further, when the lubricant leaked to the outer space adheres to the inner peripheral surface of the endless belt as described above,
There is a possibility that a slip may occur between the inner peripheral surface of the endless belt and the outer peripheral surface of the driven pulley 7a. Such slipping is not preferable because abnormal noise called squeal is generated, or the life of the endless belt and the power generation efficiency of the alternator 1 are reduced. The rotation transmission device with a built-in one-way clutch of the present invention has been made in view of the above-mentioned circumstances.

[0021]

SUMMARY OF THE INVENTION Among the rotation transmitting device with built-in one-way clutch and the method of assembling the same according to the present invention, the rotation transmitting device with built-in one-way clutch according to claim 1 is the same as that shown in FIGS. Similarly to the conventional structure shown, an inner diameter side member fixed to the end of the rotating shaft, a cylindrical outer diameter side member disposed around the inner diameter side member and concentric with the inner diameter side member, These outer diameter side members are provided between the outer peripheral surface of the member and the inner peripheral surface of the outer diameter side member only when the outer diameter side member tends to rotate relative to the inner diameter side member in a predetermined direction. A one-way clutch that enables the transmission of rotational force between the one-way clutch and an inner peripheral surface of the outer-diameter member at a position adjacent to the one-way clutch. It is provided between the bearings and supports the radial load applied to the outer diameter side member. And a support bearing for freely relative rotation between the diameter member and the outer diameter side member. The support bearing has an inner raceway on the outer peripheral surface, and has an inner race fixed on the outer peripheral surface of the inner diameter side member by press-fitting, and an outer raceway on the inner peripheral surface. An outer ring that is press-fitted into the outer peripheral surface and a plurality of rolling elements rotatably provided between the inner raceway and the outer raceway; and an outer peripheral surface of the inner race and an inner race of the outer race. Of the openings at both ends in the axial direction of the space where these rolling elements are located between the peripheral surface and at least the opening not facing the one-way clutch, the opening is closed with a seal ring. An elastic member provided on the distal end portion in the radial direction, while locking the peripheral edge portion on the proximal end side in the radial direction on the axial end portion of one of the inner race and the outer race in the axial direction. Of the sealing lip made of On the other axial end of the bearing ring mating surface provided in a state facing the axial end edge of the other race of the outer ring, thereby abut to have a fastening margin.

In particular, in the rotation transmission device with a built-in one-way clutch according to the first aspect, the one orbital ring with respect to the inner peripheral surface of the outer diameter side member and the outer peripheral surface of the inner diameter side member. The press-fitting positions of the other bearing rings in the axial direction are shifted in the direction of increasing the interference. When the present invention is carried out, the seal ring may be attached to the opening on the side opposite to the one-way clutch, as necessary, among the openings at both ends in the axial direction of the space in which the rolling elements are installed. Can be.

According to a second aspect of the present invention, there is provided the method of assembling the one-way clutch-incorporated rotation transmitting device according to the first aspect, wherein the outer ring and the inner ring constituting the support bearing are arranged in an axial direction. With the mutual positional relationship restricted to the positional relationship after completion of the one-way clutch built-in type rotation transmission device, the outer ring pressing surface portion and the inner ring axial contact surface that can freely contact the axial end surface of the outer ring are contacted. A press-fitting jig having a free inner ring pressing surface portion was prepared, and the outer ring pressing surface portion was brought into contact with the axial end surface of the outer ring, and the inner ring pressing surface portion was brought into contact with the axial end surface of the inner ring, respectively. In this state, the outer ring and the inner ring are pressed axially by the press-fitting jig to press-fit the outer ring and the inner ring into the inner peripheral surface of the outer diameter side member and the outer peripheral surface of the inner diameter side member, respectively. Perform

[0024]

According to the rotation transmission device with a built-in one-way clutch and the method of manufacturing the same according to the present invention, the rotation transmission device with a built-in one-way clutch according to the first aspect has the following features.
Regardless of the dimensional error of each part of the outer ring and the inner ring that constitute the support bearing, the seal ring assembled to the opening on the side that does not face the one-way clutch (the side that faces the external space of the one-way clutch built-in type rotation transmission device) The interference of the contact portion between the leading edge of the sealing lip and the mating surface can be sufficiently secured. For this reason, the sealing performance of the seal ring can be improved, and the lubricant sealed in the space where each ball constituting the support bearing is installed can be prevented from leaking into the external space.

In the method for assembling the rotation transmitting device with a built-in one-way clutch according to the present invention, the outer ring and the inner ring constituting the support bearing are restricted in the fitting position in the axial direction. This can be easily performed by pressing the axial end face of the inner race with a press-fitting jig. Therefore, the efficiency of the assembling work of the rotation transmission device with a built-in one-way clutch can be improved.

[0026]

1 to 3 show an embodiment of the present invention. The feature of this example is that, of the openings at both ends of the space where the balls 25, 25 constituting the support bearing 10 are installed, the side facing the external space of the pulley device with a built-in one-way clutch (roller clutch) in the assembled state. In order to sufficiently secure the sealing performance of the seal ring 26 for closing the side not facing the side 9, the method of assembling the support bearing 10 to the one-way clutch built-in type pulley device is devised. The structure and operation of the other parts are described in FIG.
Since the structure is the same as that of the conventional structure shown in FIGS. 1 to 7, the same parts are denoted by the same reference numerals, and the description of the overlapping parts will be omitted or simplified. Hereinafter, the description will focus on the characteristic parts of the present invention.

In the case of this embodiment, each of the support bearings 10
When the outer ring 22 and the inner ring 24 are press-fitted to the inner peripheral surface of the driven pulley 7a and the outer peripheral surface of the sleeve 8, respectively, the outer peripheral edge of the seal ring 26 is supported as shown in detail in FIG. The outer end surface of the outer ring 22 (the end surface facing the outer space) is made closer to the roller clutch 9 than the outer end surface of the inner ring 24 (the end surface facing the outer space) on which the mating surface 31 is formed. (Right side in FIG. 1). That is, in the case of this example, the interference λ of the contact portion between the leading edge of the seal lip 30 constituting the seal ring 26 on the side facing the external space and the mating surface 31.
The fitting position of the outer ring 22 is displaced in the axial direction with respect to the fitting position of the inner ring 24 in the direction in which is increased. Accordingly, regardless of the error of the dimensions of the outer ring 22 and the inner ring 24 (the widths of the outer ring 22 and the inner ring 24, the forming positions of the locking grooves 29 and the mating surface 31 in the axial direction, etc.), the outer space is not affected. The sealing margin λ of the contact portion between the leading edge of the seal lip 30 constituting the seal ring 26 on the side opposite to and the mating surface 31 is regulated to an appropriate range, and the sealing performance of the seal ring 26 is sufficiently ensured. ing. FIG.
Then, the seal lip 30 is set in the free state (the mating surface 3).
1 (a state in which it is not elastically deformed).

In the case of this embodiment, the axial pushing amount X (> 0) of the outer end surface of the outer race 22 with respect to the outer end surface of the inner race 24 is maintained even after the pushing is completed. Is regulated so that the axial internal gap becomes positive. Accordingly, when the outer race 22 and the inner race 24 are press-fitted in the above-described positional relationship, the rolling surfaces of the balls 25, 25 constituting the support bearing 10 are aligned with the outer race and the inner raceway 2.
1 and 23 to prevent indentations from being produced in both the tracks 21 and 23. For this reason, the pushing amount X is smaller than the axial internal clearance C of the support bearing 10 in a single state (state before assembly) (X
<C) Yes.

In this embodiment, the outer ring 22 and the inner ring 2
The press-fitting of the press-fit 4 into the inner peripheral surface of the driven pulley 7a and the outer peripheral surface of the sleeve 8 are performed using a press-in jig 32 as shown in FIG. 3 as shown in FIG. The press-fitting jig 32 is formed in a cylindrical shape with a bottom as a whole, and is a ring-shaped outer ring for pressing the outer end surface of the outer ring 22 against an outer diameter side portion of a tip end surface (a lower end surface in FIGS. 2 and 3). A pressing surface 33 for the inner ring is also provided on the inner diameter side portion, and a pressing surface 34 for the inner ring in a circular shape for pressing the outer end surface of the inner ring 24 is also provided on the inner diameter side portion.
The inner ring pressing surface portion 34 is provided so as to be recessed in the axial direction (the vertical direction in FIGS. 2 and 3) with respect to the outer ring pressing surface portion 33. The amount of depression Y in the axial direction of the inner ring pressing surface portion 34 with respect to the outer ring pressing surface portion 33 is
It is equal to the pushing amount X (Y = X).

When the outer ring 22 and the inner ring 24 are press-fitted into the inner peripheral surface of the driven pulley 7a and the outer peripheral surface of the sleeve 8 using the press-fitting jig 32 as shown in FIG.
As shown in FIG.
The outer end surfaces of the inner ring 24 are simultaneously pressed against the outer end surfaces of the inner ring 24 by the inner ring pressing surface portion 34, respectively. By pressing in this manner, the outer ring 22 and the inner ring 24 are formed.
The inner end surface of the inner race 24 (the end surface on the side facing the roller clutch 9) is located on the inner peripheral surface of the driven pulley 7a and the outer peripheral surface of the sleeve 8 on the axial end surface of the large diameter portion 12 of the sleeve 8. Press in until it hits. As a result, the fitting position of the outer ring 22 and the inner ring 24 is restricted to the state shown in FIG.

In the case of the present embodiment, after the press-fitting operation of the outer race 22 and the inner race 24 is completed as described above, the inner end surface of the outer race 22 and the end surface of the clutch outer race 14 constituting the roller clutch 9 are connected. The dimensions of each part are regulated so that a gap of the size δ is interposed between them. This prevents the inner end surface of the outer race 22 from interfering with the end of the clutch outer race 14 when the outer race 22 is press-fitted, and the clutch outer race 14 is deformed or the clutch outer race 14
Is prevented from being displaced in the axial direction.

In the case of the pulley device with a built-in one-way clutch constructed as described above, the sealing performance of the seal ring 26 on the side facing the external space can be sufficiently ensured. It is possible to prevent the grease sealed in the inside from leaking into the external space. Therefore, the durability of each of the support bearings 10 can be maintained satisfactorily, and the grease adheres to the inner peripheral surface of the endless belt, and the gap between the inner peripheral surface of the endless belt and the outer peripheral surface of the driven pulley 7a. This can prevent inconveniences such as causing slippage. or,
In the case of this example, the outer ring 2 constituting each of the support bearings 10
Regulation of the fitting position in the axial direction of the inner ring 2 and the inner ring 24 can be easily performed with the assembling work using the press-fitting jig 32 as described above. For this reason, the efficiency of the assembling work of the one-way clutch built-in type pulley device can be improved.

Incidentally, contrary to the case of the above-described embodiment,
The outer end surface of the inner ring 24 constituting the support bearing 10 is
When the inner ring 22 is pushed deeper than the outer end surface, the interference of the contact portion between the leading edge of the seal lip 30 forming the seal ring 26 on the side facing the outer space and the mating surface 31 is reduced, Alternatively, the interference may be lost and a gap may be formed between the leading edge of the seal lip 30 and the mating surface 31 as shown in FIG. When the interference is reduced or lost in this manner, the sealing performance of the seal ring 26 cannot be sufficiently ensured. Therefore, this FIG.
It is not preferable to restrict the fitting position as shown in FIG.

In practicing the present invention, the one-way clutch is not limited to the roller clutch as shown in the figure, and other types of one-way clutches such as a sprag clutch and a cam clutch can be used. is there. Further, in the above-described example, the case where a pair of support bearings is provided on both sides of the one-way clutch has been described, but it is also possible to provide only one support bearing on one side of the one-way clutch. Further, in the above-described embodiment, an example is shown in which the present invention is applied to a pulley for an alternator, but the present invention is not limited to this. For example, the present invention can be assembled to a crankshaft serving as a drive shaft of a drive device for an auxiliary machine for an automobile, or a rotating shaft of a compressor, a water pump, or a cooling fan serving as a driven shaft. Further, a gear may be used instead of the pulley as the outer diameter side member.

[0035]

As described above, the rotation transmitting device with a built-in one-way clutch and the method of manufacturing the same according to the present invention are constructed and operated as described above. The sealing performance of the seal ring assembled in the above can be sufficiently ensured. For this reason, it is possible to prevent the lubricant sealed in the space in which the balls constituting the support bearing are installed from leaking into the external space of the rotation transmission device with a built-in one-way clutch. As a result, it is possible to prevent the durability of the support bearing from deteriorating, and it is possible to prevent the inconvenience that occurs when the lubricant leaks into the external space. Further, since the fitting position of the outer ring and the inner ring constituting the support bearing can be easily regulated, the efficiency of the assembling operation can be improved.

[Brief description of the drawings]

FIG. 1 is a view similar to FIG. 7, showing a first example of an embodiment of the present invention;

FIG. 2 is a cross-sectional view shown at an intermediate stage of an assembling operation.

FIG. 3 is a sectional view of a press-fitting jig used for an assembling operation.

FIG. 4 is a view similar to FIG. 7, showing one example of an undesired structure as compared with the first example of the embodiment of the present invention;

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

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

FIG. 7 is an enlarged view of a part A of FIG.

FIG. 8 is a view similar to FIG. 7, showing an example of an assembled state in which the sealing performance of the seal ring cannot be sufficiently secured;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Alternator 2 Housing 3 Rotating shaft 4 Rolling bearing 5 Rotor 6 Commutator 7, 7a Followed pulley 8 Sleeve 9 Roller clutch 10 Support bearing 11 Screw hole part 12 Large diameter part 13 Clutch inner ring 14 Clutch outer ring 15 Roller 16 Clutch holding Container 17 Cam surface 18 Concave portion 19 Convex portion 20 Flange portion 21 Outer ring raceway 22 Outer ring 23 Inner ring raceway 24 Inner ring 25 Ball 26 Seal ring 27 Core metal 28 Elastic material 29 Lock groove 30 Seal lip 31 Mating surface 32 Press-in jig 33 For outer ring Pressing surface 34 Pressing surface for inner ring

Claims (2)

[Claims] An inner diameter side member fixed to an end of a rotating shaft;
A cylindrical outer diameter side member disposed concentrically with the inner diameter side member around the inner diameter side member, and provided between an outer peripheral surface of the inner diameter side member and an inner peripheral surface of the outer diameter side member; Only when the outer diameter side member tends to rotate relatively in a predetermined direction with respect to the inner diameter side member, a one-way clutch that can freely transmit the rotational force between the outer diameter side member and the inner diameter side member. A position adjacent to the one-way clutch is provided between the outer peripheral surface of the inner diameter side member and the inner peripheral surface of the outer diameter side member, and while supporting the radial load applied to the outer diameter side member, A support bearing that allows relative rotation between the member and the outer diameter side member, the support bearing has an inner raceway on an outer peripheral surface, and an inner ring that is externally fitted and fixed to the outer peripheral surface of the inner diameter side member by press fitting. , Having an outer raceway on the inner peripheral surface, and press-fitting on the inner peripheral surface of the outer diameter side member An outer ring to be fitted and fixed therein, and a plurality of rolling elements rotatably provided between the inner ring raceway and the outer ring raceway, and an outer peripheral surface of the inner race and an inner peripheral surface of the outer race. Of the openings in the axial direction at both ends of the space in which the rolling elements are located, at least the opening not facing the one-way clutch is closed by a seal ring. A seal lip made of an elastic material provided on an end portion in the axial direction of one of the inner race and the outer race in the axial direction of the one of the inner race and the outer race, and provided at a radially distal end portion. The other end of the inner race and the outer race is provided at the axial end of the other race so as to face the axial end of the other race so that a mating surface is provided. Rotating transmission with built-in one-way clutch In the apparatus, the press-fitting positions of the one orbital ring and the other orbital ring with respect to the inner peripheral surface of the outer diameter side member and the outer peripheral surface of the inner diameter side member in the axial direction are tightened. A rotation transmission device with a built-in one-way clutch, which is shifted in the direction to increase the margin. 2. The method for assembling a rotation transmission device with a built-in one-way clutch according to claim 1, wherein the positional relationship between an outer ring and an inner ring constituting a support bearing in the axial direction is determined by using the one-way clutch built-in type. A press-fit having an outer ring pressing surface portion capable of abutting on the axial end surface of the outer ring and an inner ring pressing surface portion capable of abutting on the axial end surface of the inner ring in a state where the rotation transmitting device is restricted to a positional relationship after completion. A jig is prepared, the outer ring pressing surface portion is brought into contact with the axial end surface of the outer ring, the inner ring pressing surface portion is brought into contact with the axial end surface of the inner ring, and the outer ring and the outer ring are pressed by the press fitting jig. Assembling a one-way clutch built-in type rotation transmission device that presses the inner ring in the axial direction to press-fit the outer ring and the inner ring into the inner peripheral surface of the outer diameter side member and the outer peripheral surface of the inner diameter side member, respectively. Method.