JP2010185547A - One-way clutch built-in type pulley device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a highly rigid one-way clutch built-in type pulley device capable of preventing expansion deformation of a retainer during high-temperature and high-speed rotation. <P>SOLUTION: An one-way clutch built-in type pulley device includes a one-way clutch 15 equipped with a clutch retainer 27 for holding a roller 26 which is made up of a plurality of lock members. The clutch retainer 27 is formed of a polyphenylene sulfide resin composition containing 20-50 mass% of glass fibers. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a pulley apparatus with a built-in one-way clutch, for example, a pulley apparatus with a built-in one-way clutch that is used by being fixed to an end of a rotating shaft such as an alternator or a compressor that is an auxiliary machine of an automobile.

  In Patent Document 1, as shown in FIG. 4, a structure of an alternator for generating electric power necessary for an automobile is described using an automobile driving engine as a drive source. In the alternator 1, the 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 fixed to a portion of the rotating shaft 3 protruding from the housing 2 at one end (right end in FIG. 4). In the assembled state to the engine, an endless belt is stretched around the driven pulley 7 so that the rotary shaft 3 can be driven to rotate by the crankshaft of the engine.

  Conventionally, as the driven pulley 7, a pulley that is simply fixed to the rotary shaft 3 has been used. On the other hand, in recent years, when the traveling speed of the endless belt is constant or increasing, it is possible to freely transmit power from the endless belt to the rotating shaft, and when the traveling speed of the endless belt is decreasing, Various types of pulley devices with built-in one-way clutches for alternators that allow relative rotation between the driven pulley and the rotating shaft have been proposed and used in part (see, for example, Patent Documents 2 to 8).

FIG. 5 shows a pulley device with a built-in one-way clutch for an alternator described in Patent Document 4. This pulley device with a built-in one-way clutch for an alternator has a sleeve 8 that can be externally fitted and fixed to the rotary shaft 3. The driven pulley 7 a around the sleeve 8 is arranged concentrically with the sleeve 8. A pair of support bearings 9 and 9 and a one-way clutch 10 are provided between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the driven pulley 7a. Of these, the support bearings 9 and 9 support the radial load applied to the driven pulley 7a and allow relative rotation between the sleeve 8 and the driven pulley 7a. Further, the one-way clutch 10 allows the rotational force from the driven pulley 7a to the sleeve 8 to be freely transmitted only when the driven pulley 7a tends to rotate relative to the sleeve 8 in a predetermined direction.

  The reason why such a one-way clutch built-in type pulley device for an ornator is used is as follows. For example, when the driving engine is a diesel engine, the fluctuation of the rotational angular speed of the crankshaft becomes large at low speeds such as idling. As a result, the traveling speed of the endless belt 11 laid over the drive pulley fixed to the end of the crankshaft also varies finely. On the other hand, the rotating shaft 3 of the alternator 1 (FIG. 4) rotated by the endless belt 11 via the driven pulley 7a is composed of the rotating shaft 3, the rotor 5 fixed to the rotating shaft 3, and the commutator 6 (FIG. 4). ), Etc., and does not change 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 against each other in accordance with fluctuations in the rotational angular velocity of the crankshaft. As a result, stress in different directions is repeatedly applied to the endless belt 11 that rubs against the driven pulley 7a, and slippage is likely to occur between the endless belt 11 and the driven pulley 7a, or the endless belt 11 May shorten the life of the product.

  Moreover, the life reduction of the endless belt 11 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 also occurs when acceleration / deceleration is repeated during traveling. That is, while the driving force is transmitted from the endless belt 11 side to the driven pulley 7a side during acceleration, the driven pulley 7a, which tries to continue to rotate based on inertia as described above, decelerates from the endless belt 11 during deceleration. A braking force is applied. The braking force and the driving force act as frictional forces in the opposite direction against the inner peripheral surface of the endless belt 11, and thus cause a decrease in the life of the endless belt 11. In particular, in the case of a vehicle equipped with an exhaust brake such as a truck, the deceleration of the rotation reduction of the crankshaft when the accelerator is off is significant, and the friction applied to the inner peripheral surface of the endless belt 11 based on the braking force As a result of the increased force, the above-mentioned decrease in life is significant.

  Therefore, by using the alternator one-way clutch built-in type pulley device as the driven pulley 7a as described above, when the traveling speed of the endless belt 11 is constant or rising, the driven pulley 7a When the traveling speed of the endless belt 11 tends to decrease, the rotation of the driven pulley 7a and the rotating shaft 3 can be freely rotated. That is, when the traveling 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 rotating shaft 3 so that the contact between the endless belt 11 and the driven pulley 7a is reduced. It prevents the contact part from rubbing strongly. In this way, the direction of the stress acting on the rubbing portion between the driven pulley 7a and the endless belt 11 is made constant, slippage occurs between the endless belt 11 and the driven pulley 7a, or the endless belt. 11 prevents the life of 11 from decreasing.

In the case of constituting the one-way clutch built-in type pulley device for an alternator as described above, as the one-way clutch 10, a roller clutch using a roller as a plurality of lock members, which is well known in the art, is generally used. A retainer made of synthetic resin (not shown in FIG. 5) for holding the lock member is provided. Conventionally, polyacetal, polyamide 46, or polyamide 66 has been used as a synthetic resin constituting the cage. When the cage is composed of these various synthetic resins, the cage can be reduced in weight, and the self-lubricating property of the cage can be sufficiently secured. Further, the cage can be easily formed by injection molding the various synthetic resins.
Further, in the roller clutch described in Patent Document 8, an example is proposed in which polyamide 9T resin is used as a resin retainer material that has little dimensional change due to water absorption and is excellent in heat resistance.

JP-A-7-139550 JP-A-56-101353 JP 7-317807 A JP-A-8-61443 Japanese Patent Publication No.7-72585 French Patent Publication FR2726059A1 JP 2000-283267 A JP 2002-139079 A

  By the way, in the pulley device with a built-in one-way clutch, the clutch inner ring of the one-way clutch is used by being attached to an alternator shaft or a compressor shaft via a sleeve, and the retainer of the one-way clutch is fixed to the clutch inner ring. The Here, the use temperature of the alternator and the compressor tends to be higher for the purpose of reducing the size of the engine room and increasing the thermal efficiency in recent years, and an engine atmosphere temperature of 130 ° C. may be required. Further, the rotational speed may reach as high as 22000 rpm, and therefore the cage is rotated at a high temperature and high speed. For this reason, the conventional synthetic resin used for a cage may expand and deform due to the influence of temperature and centrifugal force during high-temperature and high-speed rotation, and may not ensure the normal function of the one-way clutch.

  The present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide a pulley device with a built-in one-way clutch that is highly rigid and can prevent cage expansion deformation during high-temperature and high-speed rotation. It is in.

The above object of the present invention is achieved by the following configurations.
(1) a sleeve that can be externally fixed to the rotating shaft;
A driven pulley arranged concentrically with the sleeve around the sleeve;
The driven pulley is provided between the axial intermediate portion of the outer peripheral surface of these sleeves and the axial intermediate portion of the inner peripheral surface of the driven pulley, and the driven pulley only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction. A one-way clutch that freely transmits torque between the sleeve and the sleeve;
With this one-way clutch sandwiched from both sides in the axial direction, it is provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley, and supports the radial load applied to the driven pulley while relative to the sleeve and the driven pulley. In a pulley device with a built-in one-way clutch provided with a support bearing that allows rotation,
The one-way clutch includes a synthetic resin cage that holds a plurality of locking members, and the cage is a polyphenylene sulfide resin composition containing 20 to 50% by mass of glass fiber. One-way clutch built-in pulley device.

  According to the pulley apparatus with a built-in one-way clutch of the present invention, by using polyphenylene sulfide as a main component of the cage, it has excellent heat resistance and contains 20 to 50% by mass of glass fiber as a reinforcing material. Since the rigidity is increased, the cage expansion deformation at the time of high-temperature and high-speed rotation can be prevented.

The half part sectional view showing an example of an embodiment of the invention. AA sectional drawing of FIG. The half part sectional view showing the 2nd example of an embodiment of the invention. Sectional drawing which shows one example of the alternator known conventionally. Sectional drawing which shows one example of the pulley apparatus with a built-in one-way clutch for alternators conventionally known.

  1 and 2 show a first example of an embodiment of the present invention. The pulley device with a built-in one-way clutch for the alternator of this example is formed into a cylindrical shape as a whole, and is fitted around and fixed to the end of the rotating shaft 3 (see FIG. 4) of the alternator, and the periphery of the sleeve 8a. And a driven pulley 7a disposed concentrically with the sleeve 8a. Of these, the sleeve 8 a is rotatable together with the rotating shaft 3. For this purpose, in the illustrated example, a female spline portion 13 is formed on the inner peripheral surface of the intermediate portion of the sleeve 8a, and a male spline portion (not shown) formed on the female spline portion 13 and the outer peripheral surface of the end portion of the rotary shaft 3. Can be freely engaged. The structure for preventing the relative rotation between the rotary shaft 3 and the sleeve 8a may be a screw or fitting between non-cylindrical surfaces or key engagement instead of the spline.

  The driven pulley 7a provided around the sleeve 8a described above is equipped with support bearings 14a and 14b and a one-way clutch 15 described below on the inside thereof. Further, on the outer peripheral surface of the driven pulley 7a, a plurality of (four in the case of this example) concave grooves 16, 16 each having a V-shaped cross section are arranged in parallel with each other over the entire circumference. Forming. Between such a driven pulley 7a and a driving pulley (not shown), an endless structure in which a plurality of ribs (four in the case of this example) are formed on the inner peripheral surface with a V-shaped cross section extending over the entire circumference. Roll the belt.

  Between the outer peripheral surface of the sleeve 8a configured as described above and the inner peripheral surface of the driven pulley 7a configured as described above, a pair of support bearings 14a and 14b, each of which is a radial roller bearing, and a roller clutch The one-way clutch 15 is provided. In order to constitute the one-way clutch 15, the one-way clutch inner ring 17 is externally fixed by an interference fit on the outer peripheral surface of the intermediate portion of the sleeve 8 a. The one-way clutch inner ring 17 is formed in a cylindrical shape as a whole by a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415, and an outer peripheral surface is a cam surface 18 described later.

  Further, in order to form the support bearings 14a and 14b, inner rings 19 and 19 are fitted and fixed to the outer peripheral surfaces of both ends of the sleeve 8a by interference fitting. Again, each of the inner rings 19, 19 made of a hard metal plate material such as bearing steel or a carburized steel plate material such as SCM415 forms an outward flange-shaped inner ring side flange 21 at one end edge of the cylindrical portion 20. By doing so, the whole is formed in a cylindrical shape with an L-shaped cross section.

  Each of the inner rings 19, 19 is externally fitted to the sleeve 8 a with the inner ring side flange 21 positioned on the opposite side, and the respective end edges of the inner rings 19, 19 are axially opposite ends of the one-way clutch inner ring 17. It hits the edge. In the case of this example, the outer diameter of the cylindrical portion 20 of the inner rings 19, 19 is larger than the diameter of the inscribed circle related to the bottoms of the plurality of recesses 22 formed on the outer peripheral surface of the inner ring 17 for one-way clutch. is doing.

  On the other hand, the outer ring 23 is fitted and fixed to the driven pulley 7a by an interference fit. The outer ring 23 functions not only as an outer ring of the one-way clutch 15 but also as an outer ring of the support bearings 14a and 14b, and is also made of a hard metal plate material such as bearing steel or carburized steel such as SCM415. The whole is formed into a cylindrical shape by pressing the plate material. Such an outer ring 23 is formed with outer ring side flange portions 24a and 24b each having an inward flange shape at both end edges in the axial direction. Of these outer ring side flanges 24a and 24b, one (left side in FIG. 1) of the outer ring side flange 24a is formed before being combined with other constituent members. Have similar thickness dimensions. In contrast, the other (right side in FIG. 1) outer ring side flange 24b is made thin because it is formed after being combined with other constituent members.

  The one-way clutch 15 includes an inner peripheral surface of the intermediate portion of the outer ring 23 and an outer peripheral surface of the inner ring 17 for the one-way clutch. In other words, at a plurality of locations on the outer peripheral surface of the inner ring 17 for the one-way clutch, concave portions 22 and 22 that are called ramp portions and increase in depth toward one end side in the circumferential direction (right side in FIG. 2) are respectively provided. The one-way clutch inner ring 17 is formed at equal intervals in the circumferential direction along the axial direction, and the outer peripheral surface of the one-way clutch inner ring 17 serves as the cam surface 18. A cylindrical gap 25 is formed between the outer circumferential surface of the inner ring 17 for the one-way clutch and the inner circumferential surface of the outer ring 23. Of the dimensions of the cylindrical gap 25, the diameter direction of the outer ring 23 is formed. The cross-sectional height dimension with respect to each of the recesses 22 and 22 is larger than the outer diameter of the plurality of rollers 26 provided in the cylindrical gap 25, and the portion outside the recesses 22 and 22 is the above. The outer diameter of each roller 26 is smaller.

  The one-way clutch 15 includes a clutch retainer 27 formed in a saddle-shaped cylindrical shape with a synthetic resin between the inner peripheral surface of the intermediate portion of the outer ring 23 and the outer peripheral surface of the one-way clutch inner ring 17; Each has a plurality of rollers 26 and springs 28. Of these, the clutch retainer 27 engages with the concave portions 22 and 22 formed on the outer peripheral surface of the one-way clutch inner ring 17 on the inner side of the outer ring 23 with the convex portions 29 and 29 formed on the inner peripheral surface. Thus, the relative rotation with respect to the one-way clutch inner ring 17 is impossiblely mounted. Further, the one axial surface of each of the convex portions 29, 29 is opposed to the end edge of each of the inner rings 19, 19, thereby preventing the clutch retainer 27 from moving in the axial direction. The plurality of rollers 26 are held inside a pocket 30 formed in such a clutch holder 27 so as to be able to roll and slightly displace in the circumferential direction.

  Each of the springs 28 is provided between the pillar portion 31 constituting the above-described clutch retainer 27 and each of the rollers 26, and each of the rollers 26 is arranged in the same direction (see FIG. 2). The left side is elastically pressed. In general, each of the springs 28 is a stainless steel leaf spring formed by pushing back a belt-like spring plate into a U shape or a M shape, or a synthetic resin spring integrally formed with the cage.

  Each of the support bearings 14a and 14b includes the inner rings 19 and 19 and portions closer to both ends of the outer ring 23 in the axial direction. That is, the bearing cages 32, 32 formed in a bowl-shaped cylindrical shape with a synthetic resin between the outer peripheral surface of each of the inner rings 19, 19 and the inner peripheral surface of the outer ring 23 near the both axial ends. And a plurality of rollers 33a and 33b that are rotatably held by the bearing cages 32 and 32 are arranged to constitute a radial roller bearing.

  Further, floating washers 34 and 34 are respectively provided between the outer side surfaces of the outer ring side flanges 24a and 24b and the inner side surfaces of the inner ring side flanges 21 and 21, and the outer ring side flanges 24a and 24b. And the inner ring side flanges 21 and 21 are freely mounted relative to each other. Each of the floating washers 34, 34 is made of a metal having self-lubricating properties such as copper, a metal subjected to a tuftride treatment, or a metal material impregnated with a lubricating oil such as an oil-containing metal, or a polyamide resin, a polyacetal resin, or a polytetrafluoride. It is formed in an annular shape from a synthetic resin having a low coefficient of friction such as ethylene resin. Such floating washers 34, 34 are loosely sandwiched between the outer ring side flanges 24 a, 24 b and the inner ring side flanges 21, 21. The floating washers 34 and 34 are guided (prevented from radial displacement) by the outer peripheral surfaces of the inner rings 19 and 19 or the inner peripheral surface of the driven pulley 7a.

  Further, gaps between the inner peripheral surfaces of both ends in the axial direction of the outer ring 23 and the outer peripheral surfaces of the inner rings 19 and 19 are respectively closed by seal rings 35a and 35b. Each of these seal rings 35a and 35b is constituted by a core metal 36 and an elastic material 37, respectively, and the outer diameter of the elastic material 37 is elastically contracted on the inner peripheral surfaces of both ends of the outer ring 23. Supports internal fitting. Then, the tip edges of the plurality of seal lips provided on each of the elastic members 37 and 37 are slidably contacted with the outer peripheral surface of the intermediate portion of the inner rings 19 and 19 and the inner surfaces of the outer ring side flange portions 24a and 24b. It is in contact. In the case of this example, one of the seal rings 35a and 35b (on the left in FIG. 1) has one end edge of the seal ring 35a in sliding contact with the inner side surface of one outer ring side flange 24a. By abutting, positioning in the axial direction of the one seal ring 35a with respect to the outer ring 23 is achieved. On the other hand, one end edge of the seal ring 35b on the other (right side in FIG. 1) of the seal rings 35a and 35b is located between the other outer ring side flange 24b and the main body portion of the outer ring 23. It bumps into the stepped surface. At the same time, the other end edge portion of the other seal ring 35b is slidably contacted or brought into contact with the inner side surface of the other outer ring side flange portion 24b, whereby the other seal ring 35b is axially moved with respect to the outer ring 23. We aim at positioning.

  Further, on one side surface of the core bars 36, 36 of the seal rings 35a, 35b, the portions facing the end surfaces of the bearing cages 32, 32 constituting the support bearings 14a, 14b are the elastic members 37, 37 so that the sliding resistance can be kept low even if the end surfaces of the bearing retainers 32 and 32 and the one side surface of the cored bars 36 and 36 are in sliding contact with each other.

  In particular, in the case of the pulley device with a built-in one-way clutch of the present invention, the clutch retainer 27 constituting the one-way clutch 15 is a polyphenylene sulfide resin composition containing 20 to 50% by mass of glass fiber. By using polyphenylene sulfide as the main component of the cage 27, it becomes excellent in heat resistance, and the rigidity is enhanced by containing 20-50% by mass of glass fiber as a reinforcing material. The cage can be prevented from expanding and deforming. Here, when the amount of glass fiber is less than 20% by mass, there is a possibility that the predetermined rigidity and strength cannot be obtained, and when it is more than 50% by mass, the incorporation property and moldability may be lowered. There is.

  In the one-way clutch-incorporated pulley apparatus of the present invention configured as described above, the one-way clutch 15 portion is provided only with a rotational force in a predetermined direction between the driven pulley 7a having the outer ring 23 fitted and fixed therein and the rotary shaft 3. To communicate. For example, if it is assumed in FIG. 2 that the inner ring is fixed and only the outer ring 23 rotates, when the outer ring 23 rotates in the clockwise direction in the figure, the force received by each roller 26 from the inner peripheral surface of the outer ring 23 is reduced. Based on this, the concave portions 22 and 22 tend to be displaced toward the deeper side against the elasticity of the springs 28. Then, each roller 26 is in a state where it can roll within the cylindrical gap 25, and so-called overrun state in which torque is not transmitted between the outer ring 23 and the one-way clutch inner ring 17. It becomes. On the other hand, when the outer ring 23 rotates counterclockwise in FIG. 2, the rollers 26 receive the force received from the inner peripheral surface of the outer ring 23 and the elasticity of the springs 28 in FIG. As indicated by a two-dot chain line, the concave portions 22 and 22 bite into the shallower side like a wedge, and the outer ring 23 and the one-way clutch inner ring 17 are integrally coupled, and the outer ring 23 and the one-way are one-way. A so-called locked state is achieved in which the rotational force can be freely transmitted to and from the clutch inner ring 17. Regardless of fluctuations in the rotational angular velocity of the crankshaft, the direction of the stress acting on the frictional portion between the driven pulley 7a and the endless belt is made constant, and slipping occurs between the endless belt and the driven pulley 7a. Or, it is possible to prevent the life of the endless belt from being reduced.

  Particularly, in the case of the pulley device with a built-in one-way clutch of the present invention, the cage 27 constituting the one-way clutch 15 is a polyphenylene sulfide resin composition containing 20 to 50% by mass of glass fiber. Thereby, the expansion deformation of the cage can be prevented even in an environment where the engine is rotated at a high speed of about 22000 rpm at an engine ambient temperature requiring 130 ° C. In addition, since each of the cages 27 is made of the above-described synthetic resin, the cage 27 is lightened, the self-lubricating property of the cage 27 is sufficiently secured, and the above-described synthetic resin is injected. The cage 27 can be easily formed by molding. Incidentally, in addition to the clutch retainer 27, the bearing retainers 32 and 32 constituting the respective support bearings 14a and 14b can be similarly formed by using a polyphenylene sulfide resin composition containing 20 to 50% by mass of glass fiber. There is an effect.

  In the case of this example, the same pair of inner rings 19 and 19 that are externally fitted and fixed to both ends of the sleeve 8a are used. Accordingly, the outer diameters of the inner rings 19, 19 constituting the pair of support bearings 14a, 14b are the same. On the other hand, since the outer ring 23 used for the pair of support bearings 14a and 14b requires a draft angle when performing press working, the inner diameter of the outer ring 23 is the one outer ring side flange 24a. From the side on which the outer ring is formed toward the side on which the other outer ring side flange 24b is formed. Therefore, the pair of support bearings 14a and 14b have different diameter dimensions of the cylindrical gaps 38a and 38b between the inner peripheral surfaces of both ends of the outer ring 23 and the outer peripheral surfaces of the inner rings 19 and 19 (right side in FIG. 1). The cylindrical gap 38b is slightly larger than the left cylindrical gap 38a). On the other hand, in order to support the radial load almost uniformly on both sides in the axial direction of the driven pulley 7a, the radial gaps in the support bearings 14a and 14b need to be substantially the same. Therefore, in the case of this example, the outer diameters of the plurality of rollers 33a constituting one (left side in FIG. 1) of the support bearings 14a and the plurality of rollers (a right side in FIG. 1) constituting the support bearings 14b. The outer diameter of the roller 33b is about 5 μm smaller. The radial gaps in the pair of support bearings 14a and 14b are both about 30 μm.

  Further, when the outer diameters of the rollers 33a and 33b are made different from each other in the support bearings 14a and 14b in this way, in the actual assembly work, the subtle differences in the outer diameters of the rollers 33a and 33b are changed. It is difficult for a person to judge and to assemble each support bearing 14a, 14b on the appropriate side in the outer ring 23. For this reason, in the case of this example, among the pair of support bearings 14a and 14b, the bearing retainer 32 constituting one of the support bearings 14a (14b) is colored, or both the support bearings 14a, The colors of the bearing cages 32 and 32 constituting 14b are different from each other. Thereby, the operator can easily perform the operation of assembling the support bearings 14a and 14b on the appropriate side in the outer ring 23.

  Next, FIG. 3 shows a second example of the embodiment of the present invention. In the case of this example, a pair of support bearings 39 and 39 each of which is a deep groove type ball bearing and one roller clutch are provided between the outer peripheral surface of the sleeve 8a and the inner peripheral surface of the driven pulley 7a. 1-way clutch 15a. The pair of support bearings 39, 39 each includes an outer ring 41 having a deep groove type outer ring raceway 40 on the inner peripheral surface, an inner ring 43 having a deep groove type inner ring raceway 42 on the outer peripheral surface, and the outer ring raceway 40. A plurality of balls 44 and 44 which are rolling elements provided in a freely rotatable manner between the inner ring raceway 42 and a crown shape made of a synthetic resin which holds each of the balls 44 and 44 so as to freely roll. Bearing retainer 32a. Each of the support bearings 39, 39 has an outer ring 41 fitted and fixed to both ends of the inner peripheral surface of the driven pulley 7a by an interference fit, and each inner ring 43 is tightened to both ends of the outer peripheral surface of the sleeve 8a. By being externally fitted and fixed by fitting, it is provided between both ends of the outer peripheral surface of the sleeve 8a and both ends of the inner peripheral surface of the driven pulley 7a. In the case of this example, the inner ring 43 and the outer ring 41 are fitted and fixed to the sleeve 8a and the driven pulley 7a by an interference fit. For this reason, there is a possibility that the reduction amount of the radial gap in each of the support bearings 39 and 39 becomes so large that it cannot be ignored based on the tightening allowance for fitting and fixing. For this reason, for these support bearings 39, 39, those having an initial radial clearance as large as about C5 are used. Based on the fitting of the inner ring 43 and the outer ring 41 with the sleeve 8a and the driven pulley 7a, even if the radial gaps of the support bearings 39 and 39 are reduced, the radial gaps are prevented from becoming negative. Further, the one-way clutch 15a is provided between the outer peripheral surface intermediate portion of the sleeve 8a and the inner peripheral surface intermediate portion of the driven pulley 7a. In the case of this example, the one-way clutch outer ring 45 constituting the one-way clutch 15a is provided separately from the outer rings 41, 41 constituting the pair of support bearings 39, 39.

Also in this example, the clutch cage 27 constituting the one-way clutch 15a is made of a polyphenylene sulfide resin composition containing 20 to 50% by mass of glass fiber. Thereby, the expansion deformation of the cage can be prevented even under an environment where the engine is rotated at a high speed of about 22000 rpm at an engine ambient temperature requiring 130 ° C.
Since other configurations and operations are the same as in the case of the first example described above, the same parts are denoted by the same reference numerals, and overlapping illustrations and descriptions are omitted.

  In each of the above-described examples, the one-way clutch has been described as a roller clutch that uses rollers as a plurality of locking members. However, the present invention is not limited to such a structure, and the present invention can also be applied to a structure in which a one-way clutch is a sprag type one-way clutch that uses sprags as a plurality of locking members. . In each of the above-described examples, the structure using the cage for both the one-way clutch and the support bearing has been described. However, at least one of the one-way clutch and the support bearing is a cage. The present invention can be applied to such a structure even if it is a structure that does not use.

DESCRIPTION OF SYMBOLS 1 Alternator 2 Housing 3 Rotating shaft 4 Rolling bearing 5 Rotor 6 Commutator 7, 7a Driven pulley 8, 8a Sleeve 9 Support bearing 10 One-way clutch 11 Endless belt 12 Rolling body 13 Female spline part 14a, 14b Support bearing 15, 15a Directional clutch 16 Concave groove 17 Inner ring 18 for one-way clutch Cam surface 19 Inner ring 20 Cylindrical portion 21 Inner ring side flange 22 Recess 23 Outer ring 24a, 24b Outer ring side flange 25 Cylindrical gap 26 Roller 27 Clutch retainer 28 Spring 29 Convex Part 30 Pocket 31 Column part 32, 32a Bearing cage 33a, 33b Roller 34 Floating washers 35a, 35b Seal ring 36 Core metal 37 Elastic material 38a, 38b Cylindrical gap 39 Support bearing 40 Outer ring raceway 41 Outer ring 42 Inner ring raceway 43 Inner ring 44 ball 45 one-way clutch outside

Claims (1)

A sleeve that can be externally fixed to the rotating shaft;
A driven pulley arranged concentrically with the sleeve around the sleeve;
The driven pulley is provided between the axial intermediate portion of the outer peripheral surface of these sleeves and the axial intermediate portion of the inner peripheral surface of the driven pulley, and the driven pulley only when the driven pulley tends to rotate relative to the sleeve in a predetermined direction. A one-way clutch that freely transmits torque between the sleeve and the sleeve;
With this one-way clutch sandwiched from both sides in the axial direction, it is provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the driven pulley, and supports the radial load applied to the driven pulley while relative to the sleeve and the driven pulley. In a pulley device with a built-in one-way clutch provided with a support bearing that allows rotation,
The one-way clutch includes a synthetic resin cage that holds a plurality of locking members, and the cage is a polyphenylene sulfide resin composition containing 20 to 50% by mass of glass fiber. One-way clutch built-in pulley device.

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