JP2000161471A - Pulley device with built-in one-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve reliability and durability by providing a cam clutch serving as a one-way clutch between a portion on the outer circumferential surface of a sleeve apart from a support bearing and a portion on the inner circumferential surface of a pulley apart from the support bearing. SOLUTION: A pair of support bearings 3, 3 and a cam clutch serving as a one-way clutch 4 both of which are deep groove type ball bearings are provided between the inner circumferential surface of a pulley 1 formed in a cylindrical shape and a cylindrical sleeve 2. The cam clutch 4 is mounted with a gap interposed between both end surfaces in the axial direction, an end surface of a stepped part 12 formed on the outer circumferential surface at one end of the sleeve 2 and an end surface of an intermediate seat 13 around which an inner race constituting any one of the support bearings 3. With this constitution wherein such a cam clutch 4 whose wear resistance is exellent is used as the one-way clutch, the purpose is attained.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION A pulley device incorporating a one-way clutch according to the present invention is fixed to, for example, an end of an input shaft of an alternator which is a kind of auxiliary equipment for an engine, and is fixed to an end of a crankshaft of the engine. The alternator is used to drive the alternator by extending a belt between the driven pulleys.

[0002]

2. Description of the Related Art An engine accessory such as an alternator is driven by, for example, a belt partially extending over a drive pulley fixed to an end of a crankshaft of a drive engine of an automobile. That is, an endless belt is stretched between the driven pulley fixed to the end of the input shaft of the engine accessory and the drive pulley, and the engine accessory is rotatable in synchronization with the drive engine. .

Conventionally, as the driven pulley, a pulley simply fixed to the input shaft has been used. On the other hand, in recent years, when the running speed of the belt is constant or increasing, the power can be freely transmitted from the belt to the input shaft. Various roller clutch-incorporated pulley devices that incorporate a roller clutch as a one-way clutch and that can freely rotate relative to a shaft have been proposed and used in part. For example, JP-A-7-31807-8 and JP-A-8-31807
JP-A-61443, JP-B-7-72585, French Patent Publication FR2726059A1, and the like describe a pulley device with a built-in roller clutch having the above-described functions.

The pulley devices with a built-in roller clutch described in each of these documents have a sleeve which can be externally fitted and fixed to an input shaft, and a pulley having a cylindrical inner peripheral surface is provided around the sleeve. And are arranged concentrically. A pair of support bearings and a roller clutch are provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley. Among these, the support bearing allows the sleeve and the pulley to rotate relative to each other while supporting the radial load applied to the pulley. Also, the roller clutch allows the transmission of the rotational force from the pulley to the sleeve only when the pulley rotates in a predetermined direction with respect to the sleeve.

The reason for using such a pulley device with a built-in roller clutch is as follows. For example, when the driving engine is a diesel engine, the fluctuation width W of the angular velocity of the crankshaft becomes large as shown in FIG. 15 at the time of low rotation such as idling. As a result, the running speed of the endless belt stretched over the driving pulley also fluctuates finely. On the other hand, the input shaft of the alternator driven to rotate by the endless belt via the driven pulley does not fluctuate so rapidly because of the inertia mass of the input shaft and the rotor fixed to the input shaft. Therefore, when the driven pulley is simply fixed to the input shaft, the endless belt and the driven pulley tend to rub in both directions due to a change in the angular speed of the crankshaft. As a result, stress is repeatedly applied to the endless belt that rubs with the driven pulley in different directions, so that slippage easily occurs between the endless belt and the driven pulley,
Alternatively, the life of the endless belt may be shortened.

Therefore, by using the above-mentioned roller clutch built-in type pulley device as such a driven pulley,
When the traveling speed of the endless belt is constant or increasing, the transmission of the rotational force from the driven pulley to the input shaft is free.On the contrary, when the traveling speed of the endless belt tends to decrease, The relative rotation between these driven pulleys and the input shaft is made free. That is, when the angular velocity of the pulley over which the endless belt is wound changes as shown by a broken line α in FIG. 16, the angular velocity of the input shaft on which the roller clutch built-in type pulley device is assembled changes as shown by a solid line β in FIG. I do. Of the solid line β, in the linear regions γ, γ that deviate from the dashed line α, the roller clutch is overrun. And
The roller clutch changes from the overrun state to the connected state at point x, x, at which each of the linear regions γ, γ ends. As described above, when the traveling speed of the endless belt tends to decrease, the angular speed of the driven pulley is made slower than the angular speed of the input shaft, and the contact portion between the endless belt and the driven pulley rubs strongly. Prevent things. As a result, the direction of the stress acting on the rubbed portion between the driven pulley and the endless belt becomes constant, slippage occurs between the endless belt and the driven pulley, or the life of the endless belt is reduced. To prevent

[0007]

In the case of a conventional pulley device having a built-in one-way clutch, a roller clutch is used as the one-way clutch. Therefore, when the size is reduced, sufficient durability is always ensured. Things are difficult. The cause is that the roller clutch changes from the overrun state to the connected state when the running speed of the endless belt shifts from a decreasing trend to an increasing trend.At the moment of this change, the angular speed of the rotating shaft such as the input shaft suddenly changes. To do that. That is, x, x in FIG.
At this point, the angular velocity of the rotating shaft changes rapidly (rapidly increases). Based on this sudden change, an impact load is applied to the plurality of rollers, the outer ring, and the inner ring that constitute the roller clutch, thereby deteriorating the durability of the roller clutch. The pulley device incorporating the one-way clutch of the present invention has been invented in view of the above-described circumstances.

[0008]

SUMMARY OF THE INVENTION A pulley device incorporating a one-way clutch according to the present invention, like a pulley device incorporating a one-way clutch known in the art, includes a sleeve which can be externally fitted and fixed to a rotating shaft. A pulley disposed concentrically with the sleeve around the sleeve, and provided between an outer peripheral surface of the sleeve and an inner peripheral surface of the pulley, and supporting the radial load applied to the pulley while supporting the pulley relative to the sleeve. A support bearing that can rotate freely, and only a rotational force in one direction provided between a portion of the outer peripheral surface of the sleeve that deviates from the support bearing and a portion of the inner peripheral surface of the pulley that deviates from the support bearing. And a one-way clutch for transmitting torque. In particular, in the pulley device incorporating the one-way clutch of the present invention, the one-way clutch is a cam clutch.

[0009]

In the pulley device incorporating the one-way clutch of the present invention constructed as described above, the one-way clutch is superior in performance such as wear resistance as compared with a conventionally used roller clutch. Since a cam clutch is used, reliability and durability can be improved.

[0010]

1 to 4 show a first embodiment of the present invention. An inner peripheral surface of a pulley 1 formed in a cylindrical shape to span an intermediate portion of an endless belt (not shown);
A pair of support bearings 3, 3 each of which is a deep groove ball bearing between a cylindrical sleeve 2 which is externally fitted and fixed to an end portion or an intermediate portion of a rotating shaft (not shown) such as an input shaft of an alternator. And a cam clutch 4 which is a one-way clutch. The cam clutch 4 has two end surfaces in the axial direction, an end surface of a step 12 formed on the outer peripheral surface of one end (left end in FIG. 1) of the sleeve 2 and one of the support bearings 3.
Is provided in a state where a gap is interposed between the inner ring and the end face of the spacer 13 to which the inner race is externally fitted and fixed. In the case where the end face of the cam clutch 4 is an inner ring constituting a retaining ring or a support bearing as in another embodiment described later, this end face and one side of the retaining ring or the inner ring are used. A gap is interposed between the end face of the base and the end face of the base.

On the other hand, a spline hole or a screw hole is formed in an intermediate portion of the inner surface of the sleeve 2 so that the end or the intermediate portion of the rotating shaft can be fixed in the sleeve 2 so as not to rotate relatively. . In order to form the spline holes or screw holes, at least a portion of the inner peripheral surface of the sleeve 2 is subjected to a carburizing treatment, and as described later, when the outer peripheral surface of the sleeve 2 is subjected to a carburizing heat treatment. This also prevents the portion from becoming hard. The inner ring that constitutes one of the support bearings 3 (the left side in FIG. 1) of the pair of support bearings 3 is externally fixed to the outer peripheral surface of the step portion 12 by interference fitting. On the other hand, the other (right side of FIG. 1)
The inner ring constituting the support bearing 3 is externally fitted and fixed to the outer peripheral surface of the spacer 13 which is externally fitted and fixed to the other end (the right end in FIG. 1) of the sleeve 2.

The cam clutch 4 comprises a combination of a retainer 5 as shown in FIG. 3, a plurality of cams 6, 6, and a garter spring 7 for bundling the plurality of cams 6, 6. The retainer 5 includes a pair of rim portions 8, 8 each having an L-shaped cross section, and a plurality of pillar portions 9, 9 connecting the inner side portions of the inner surfaces of both rim portions 8, 8. Consists of These pillars 9, 9 are arranged at regular intervals in the circumferential direction, and four circumferences are surrounded by the pillars 9, 9 adjacent to each other in the circumferential direction and the pair of rims 8, 8. Part
The pockets are 10 and 10, respectively. Each of the cams 6, 6 is held in each of the pockets 10, 10 so as to be swingably displaceable.

As described above, the retainer 5 holding the cams 6, 6 so as to be able to swing and displace is provided with a slight gap in the axial direction between the step 12 and the spacer 13. It is provided in the state where it is made to be. The retainer 5 is externally fitted to the sleeve 2 by intermediate fitting. That is, the retainer 5 does not rattle with respect to the sleeve 2, but is externally fitted in a state where a large frictional force does not act on the fitting portion.
Therefore, the retainer 5 rotates relative to the sleeve 2 when a circumferential force is applied.

Each of the cams 6, 6 is of an engagement type as shown in detail in FIG. According to the positional relationship between the point of contact with the outer peripheral surface of the sleeve 2 which is a cylindrical surface and the center of gravity G, the centrifugal force caused by the revolving motion of this type of cam 6 is reduced by the pulley 1 and the outer peripheral surface of the cylindrical cam 6. Act in a direction in which the inner peripheral surface of the first member comes into contact with the inner peripheral surface. The cams 6, 6 each having a shape as shown in detail in FIG. 4, are held one by one in the pockets 10, 10 of the retainer 5 so as to be swingable. The garter spring 7 is inserted into an engagement groove 11 formed at an intermediate portion in the thickness direction (the left-right direction in FIG. 1) of each of the cams 6. The garter spring 7 has elasticity in the direction of shortening the overall length, and the contact portion between the garter spring 7 and the bottom surface of each of the engagement grooves 11, 11 is formed by the outer peripheral surface of the cam 6 and the outer peripheral surface of the sleeve 2. With respect to the point of contact with the surface, the portion where the outer peripheral surface of the cam 6 and the inner peripheral surface of the pulley 1 are in contact exists on the opposite side in the circumferential direction. Therefore, the garter spring 7 elastically urges each of the cams 6, 6 in a direction in which the outer peripheral surface of each of the cams 6, 6 comes into contact with the inner peripheral surface of the pulley 1.

The inner peripheral surface of the pulley 1, which is the raceway surface engaged with the outer peripheral surface of each of the cams 6, 6, has a surface hardness of HRc 55 or more by high frequency quenching. Further, the outer peripheral surface of the sleeve 2, which is the raceway surface engaged with the outer peripheral surface of each of the cams 6, 6, is subjected to a carburizing and quenching treatment to have a surface hardness of HRc 55 or more.

The space 14 in which the cam clutch 4 constructed as described above is incorporated is filled with a lubricant for lubricating the contact portions between the components of the cam clutch 4 and preventing wear. I have. As such a lubricant, preferably 12
Oil or grease that forms a good oil film even in a temperature range exceeding 0 ° C (for example, urea or diurea is used as a thickener and ester-based synthetic oil is used as a base oil), or traction at 120 ° C It is preferable to use traction oil or traction grease having a coefficient exceeding 0.05. If such traction oil or traction grease is used, a sufficient oil film is formed on each of the contact portions, regardless of the large surface pressure acting on the contact portions between the peripheral surfaces during meshing, and the fretting wear is reduced. In addition to the prevention, the cam clutch 4 can transmit power without slipping during rotation in the meshing direction. When grease is used as a lubricant to fill the space 14, fretting wear can be more effectively prevented if the consistency is in the range of 310 to 340.

Also, when the cam clutch 4 is engaged, the outer race and the inner race of the support bearings 3 and 3 do not rotate relative to each other, and the rolling surfaces of the rolling elements contact the outer raceway and the inner raceway at the same portion. Vibration is received while in the state. For this reason, fretting wear is likely to occur at this contact portion. In view of such circumstances, as a lubricant for lubricating each of the support bearings 3, 3, an oil or grease that forms a good oil film even in a temperature range exceeding 140 ° C. (for example, urea, diurea as a thickener) It is preferable to use an ester-based synthetic oil as the base oil, and preferably to use a base oil having a viscosity at 40 ° C. of 60 cSt or less.

In any case, in order to prevent the leakage of the lubricant as described above, a seal ring is provided at a position sandwiching the space 14 from both sides in the axial direction. In the illustrated example, the seal ring is used as the seal ring. Seal rings 15, 15 incorporated in a pair of support bearings 3, 3 are used. If the same lubricant as that for lubricating the support bearings 3 is used as the lubricant for lubricating the cam clutch 4, one lubricant is used for each of the support bearings 3. Of the seal rings 15 provided for each pair, the seal rings 15 provided on the space 14 side may be omitted.

The pulley device incorporating the one-way clutch of the present invention constructed as described above is mounted, for example, at the end of the input shaft of an alternator, and between the drive pulley fixed to the end of the crankshaft of the engine. The operation when the alternator is rotationally driven by the stretched endless belt is substantially the same as that of the above-described conventionally known pulley device having a built-in roller clutch. That is, when the running speed of the endless belt is constant or increasing, the transmission of the rotational force from the pulley 1 to the sleeve 2 externally fixed to an input shaft (not shown) is allowed. On the other hand, when the running speed of the endless belt tends to decrease, the relative rotation between the pulley 1 and the sleeve 2 is made freely. A radial load is applied to the pulley 1 based on the tension of the endless belt.
The above-mentioned pair of support bearings 3, 3 support. Therefore, since the radial load applied to the cam clutch 4 which is a one-way clutch is limited, the durability of the cam clutch 4 can be sufficiently ensured.

More specifically, the radial load applied to the pulley 1 based on the tension applied to the endless belt is supported by the pair of support bearings 3, and the rotation from the pulley 1 to the sleeve 2 is performed. The force is transmitted by frictionally engaging the outer peripheral surfaces of the plurality of cams 6 with the inner peripheral surface of the pulley 1 and the outer peripheral surface of the sleeve 2, each of which is a cylindrical surface. When the angular speed of the crankshaft of the engine fluctuates greatly as shown in FIG. 15 described above, when the angular speed decreases, the distance between the outer peripheral surface of each of the cams 6, 6 and the inner peripheral surface of the pulley 1 and the outer peripheral surface of the sleeve 2 is reduced. As the frictional force is reduced or lost, the sleeve 2 idles and releases the inertial mass of the alternator. Then, the contact portion between the endless belt and the outer peripheral surface of the pulley 1 is prevented from being strongly rubbed, and slippage occurs between the endless belt and the pulley 1 or the life of the endless belt is shortened. To prevent On the other hand, when the angular velocity increases again and the relative rotational speed between the sleeve 2 and the pulley 1 becomes zero,
The outer peripheral surface of each of the cams 6, 6 frictionally engages with (engages with) the inner peripheral surface of the pulley 1 and the outer peripheral surface of the sleeve 2 to transmit the power of the endless belt to the sleeve 2 again. .

In particular, in the case of the present invention, the cam clutch 4 which is superior in performance such as abrasion resistance as compared with the roller clutch which has been conventionally used is used as the one-way clutch. And durability can be improved. In addition, in the case of this example, the contact positions of the outer peripheral surfaces of the cams 6, 6 with the inner peripheral surface of the pulley 1 and the outer peripheral surface of the sleeve 2 are slightly shifted with the operation of the pulley device. That is, as described above, the retainer 5 rotates relative to the sleeve 2 when a force is applied in the circumferential direction. As a result, the contact positions vary uniformly over the entire circumference of the inner peripheral surface of the pulley 1 and the outer peripheral surface of the sleeve 2, and it is possible to prevent wear from progressing only on a part of both peripheral surfaces. Such an operation and effect can be obtained by using the cam clutch 4 as a one-way clutch.
It cannot be obtained when a roller clutch is used as in the conventional structure. In addition, the outer peripheral surface of the sleeve 2 is hardened by nitriding not only the portion that engages with the outer peripheral surface of each of the cams 6 and 6 but also the portion that rubs with the inner peripheral surface of the cage 5 to prevent wear. Is being planned. Similarly, the cage 5
The inner peripheral surface is also subjected to a surface treatment to prevent abrasion, if necessary.

The diameter of the pulley 1 provided on the input shaft side of the alternator is smaller than the diameter of the drive pulley provided on the crankshaft side, and the alternator is used at an increased speed with respect to the rotation speed of the engine. It is common. Therefore, the alternator is 15000 r.p.
m. When the alternator rotates at such a high speed, lubricant such as grease sealed in the pulley device collects on the inner peripheral surface side of the pulley 1 due to centrifugal force. As a result, the lubricity based on this lubricant is
On the inner peripheral surface side of the pulley 1, it becomes better, but on the outer peripheral surface side of the sleeve 2, it tends to be defective. Therefore, during operation of the pulley device incorporating the one-way clutch of the present invention, when the cam clutch 4 is idling, the outer peripheral surfaces of the cams 6 and 6 and the inner peripheral surface of the pulley 1 are slid. It is preferable that the outer peripheral surface of 6, 6 and the outer peripheral surface of the sleeve 2 do not slip. Due to such circumstances, in the illustrated example, the retainer 5 for holding the above-mentioned respective cams 6 is replaced with the above-mentioned sleeve 2.
The cam clutches 6 and 6 are limited in that they can be displaced in the circumferential direction of the sleeve 2 (with an intermediate fit so as to have a resistance against being displaced in the circumferential direction). When the idler 4 rotates, the outer peripheral surfaces of the cams 6 and 6 and the inner peripheral surface of the pulley 1 slide.

Since the alternator rotates at a high speed as described above, the seal rings 15 and 15 are rotated based on centrifugal force.
Care must be taken to prevent lubricants such as oil and grease from leaking from the part. For this purpose, for example, a groove for venting air is not provided in each of the seal rings 15, 15, or even when it is provided, it is provided on the seal lip portion on the inner peripheral edge side. Further, in the case where grease is sealed, the grease sealing ratio is set to 20% of the space volume in both the internal space of each of the support bearings 3 and the space 14 in which the cam clutch 4 is installed so that the amount of the grease is not too large. Keep within the range of ~ 35%. When the same type is used for the internal space of each of the support bearings 3 and the space 14 in which the cam clutch 4 is installed, and when the seal rings 15 and 15 on the space 14 side are omitted, grease is used. Is 20 to 35% of the volume of the space between the remaining seal rings 15, 15.
And

Next, FIG. 5 shows a second embodiment of the present invention.
An example is shown. In the case of this example, the inner ring 16 constituting the support bearing 3a provided on the other end side of the sleeve 2 (on the side opposite to the step portion 12 and on the right side in FIG. 5) is made thick and provided in the first example described above. The spacer 13 (FIG. 1) that has been used is omitted. By adopting such a structure, the spacer 13 becomes unnecessary,
The number of parts is reduced. The other configurations and operations are the same as those of the first example described above, and therefore, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

Next, FIG. 6 shows a third embodiment of the present invention.
An example is shown. In the case of this example, the support bearing 3 provided on one end side of the sleeve 2 (on the side of the step portion 12 and on the left side in FIG. 6).
The outer raceway 18 constituting b is formed directly on the inner peripheral surface of the pulley 1. By adopting such a structure, the outer ring for forming the support bearing 3b is not required, and the number of parts is reduced, and at the same time, the degree of freedom in designing the seal ring 15 mounted on the support bearing 3b is improved. Is being planned. Other configurations and operations are the same as those in the above-described second example, so that the same reference numerals are given to the same parts, and
A duplicate description will be omitted.

FIG. 7 shows a fourth embodiment of the present invention.
An example is shown. In the case of this example, the outer raceway 18 constituting the support bearing 3c provided on the other end side of the sleeve 2 (on the opposite side of the step portion 12 and on the right side in FIG. 7) is formed directly on the inner peripheral surface of the pulley 1. ing. By adopting such a structure, the outer ring for constituting the support bearing 3c is not required, and the number of parts is reduced, and at the same time, the degree of freedom in designing the seal ring 15 mounted on the support bearing 3c is improved. Is being planned. Other configurations and operations are the same as those of the third embodiment.
Since this is the same as in the case of the example, the same reference numerals are given to the same parts, and the duplicate description will be omitted.

Next, FIG. 8 shows a fifth embodiment of the present invention.
An example is shown. In the case of this example, the pair of support bearings 3 and 3 are mounted on one half (the left half in FIG. 8) of the pulley 1 and the sleeve 2, and the cam clutch 4 is mounted on the other half (the right half in FIG. 8). ). For this reason, in the case of the present embodiment, a seal ring 19 for closing the end opening of the space 14a accommodating the cam clutch 4 is provided separately from the seal rings 15, 15 incorporated in the support bearings 3, 3. Is provided. Also, a retaining ring 21 for preventing the retainer 5 constituting the cam clutch 4 from shifting in the axial direction is provided.
The sleeve 2 is locked to a portion near the other end. In the case of such a structure of this example, the pair of support bearings 3,
3 can be easily assembled between the inner peripheral surface of the pulley 1 and the outer peripheral surface of the sleeve 2 as compared with the above-described examples. Other configurations and operations are the same as those of the first example described above. Therefore, the same reference numerals are given to the same parts, and the duplicate description will be omitted.

Next, FIG. 9 shows a sixth embodiment of the present invention.
An example is shown. In the case of this example, a belt groove 20 for passing the V-belt is formed in one half (the left half in FIG. 9) of the outer peripheral surface of the pulley 1a. A pair of support bearings 3, 3 are provided at positions sandwiching the widthwise intermediate portion of the belt groove 20, and both support bearings 3, 3 are provided with the V bearing.
The radial load applied from the belt is evenly supported. By arranging the pair of support bearings 3, 3 for supporting the radial load applied from the narrow V-belt in this way, the balance of the force applied to the pulley device having a built-in one-way clutch is improved. Can be improved in durability. Other configurations and operations are the same as in the case of the above-described fifth example.
A duplicate description will be omitted.

Next, FIG. 10 shows a seventh embodiment of the present invention. In the case of this example, since two V belts are wound around the outer peripheral surface of the pulley 1b, two belt grooves 2 are provided.
0 and 20 are formed. Other configurations and operations are the same as those of the first example described above. Therefore, the same reference numerals are given to the same parts, and the duplicate description will be omitted.

FIG. 11 shows an eighth embodiment of the present invention. In the case of this example, the support bearing 3
The inner rings 16, 16 a constituting 3 a are
The outer ring is fitted by a clearance fit or an intermediate fit, and the retaining rings 21 are used to prevent the axial displacement. On the other hand, the outer races of the support bearings 3 and 3a are fixed to the pulley 1 by interference fit. Other configurations and operations are the same as those of the above-described second example shown in FIG. The structure for supporting the inner ring of each support bearing with respect to the sleeve 2 as in this example can be combined with other embodiments.

Next, FIG. 12 shows a ninth embodiment of the present invention. In the case of this example, the retainer 5 is omitted from the structure of the first example shown in FIG. That is,
In the case of this example, the cam clutch 4a is composed of a plurality of cams 6, 6 and a garter spring 7. These cams 6 are guided by the end face of the step portion 12 and the end face of the spacer 13 provided on both axial sides of the cam clutch 4a. Also, the inner diameter of the pulley 1, the outer diameter of the sleeve 2,
In addition, the shape of each of the cams 6, 6 is appropriately regulated, and the cams 6, 6 which are adjacent in the circumferential direction regulate (guide) each other in the circumferential position. In this way, the cage 5
By constructing the cam clutch 4a having no one-way clutch, the weight and cost of the pulley device incorporating the one-way clutch can be reduced.

Next, FIG. 13 shows a tenth embodiment of the present invention. In the case of the present example, a step surface 22 is provided on the outer peripheral surface of the sleeve 2 on the side opposite to the step portion 12, and the end surface of the inner ring 16 a of the support bearing 3 is abutted against the step surface 22, and In the axial direction. Therefore, a step surface for positioning the support bearing 3 is not required on the inner peripheral surface side of the pulley 1, and the inner diameter of the pulley 1 can be reduced at the step surface 22 side. With such a configuration, the diameter of the support bearing 3 can be reduced without sacrificing the assemblability of the pulley device incorporating the one-way clutch.
It is designed to be easily designed. In the illustrated example, the cam clutch 4a having no retainer is used, but a cam clutch having a retainer may be used. Other configurations and operations are the same as those of the above-described eighth example shown in FIG.

FIG. 14 shows an eleventh embodiment of the present invention. In the case of this example, a hard metal liner 23 that is in contact with the outer peripheral surfaces of the cams 6 and 6 of the cam clutch 4 is fitted and fixed to the inner peripheral surface of the pulley 1. Since such a liner 23 is used, the pulley 1 does not need to be hardened by quenching or the like. Such a hard metal liner may be provided on the outer peripheral surface of the sleeve 2 instead of the inner peripheral surface of the pulley 1 or together with the inner peripheral surface of the pulley 1. Of course, in this case, there is no need to cure the sleeve 2 itself. Other configurations and operations are the same as in the above-described tenth example.

[0034]

The pulley device incorporating the one-way clutch according to the present invention is constructed and operates as described above, so that even under severe use conditions, excellent durability is ensured, and the durability of the endless belt is maintained. A practical structure that can be improved can be realized.

[Brief description of the drawings]

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

FIG. 2 is a cross-sectional view taken along line AA of FIG.

FIG. 3 is a perspective view of a retainer.

FIG. 4 is an enlarged view of a portion B in FIG. 2;

FIG. 5 is a sectional view showing a second example of the embodiment of the present invention.

FIG. 6 is a sectional view showing the third example.

FIG. 7 is a sectional view showing the fourth example.

FIG. 8 is a sectional view showing the fifth example.

FIG. 9 is a sectional view showing a sixth example.

FIG. 10 is a sectional view showing a seventh example.

FIG. 11 is a sectional view showing the eighth example.

FIG. 12 is a sectional view showing a ninth example;

FIG. 13 is a sectional view showing the tenth example.

FIG. 14 is a sectional view showing the eleventh example.

FIG. 15 is a diagram showing a change state of an angular velocity of a crankshaft of an engine that drives a pulley.

FIG. 16 is a diagram showing a change state of an angular velocity of a pulley driven via an endless belt by a crankshaft of an engine and an angular velocity of a rotating shaft to which a pulley device incorporating a one-way clutch is assembled.

[Explanation of symbols]

 1, 1a, 1b pulley 2 sleeve 3, 3a, 3b, 3c support bearing 4, 4a cam clutch 5 retainer 6 cam 7 garter spring 8 rim 9 pillar 10 pocket 11 engaging groove 12 step 13 spacer 13 14a Space 15 Seal ring 16, 16a Inner ring 18 Outer ring raceway 19 Seal ring 20 Belt groove 21 Retaining ring 22 Step surface 23 Liner

Claims (1)

[Claims] 1. A sleeve which can be externally fitted and fixed to a rotating shaft, a pulley disposed concentrically with the sleeve around the sleeve, and a pulley provided between an outer peripheral surface of the sleeve and an inner peripheral surface of the pulley. A bearing that allows the relative rotation of these sleeves and pulleys while supporting the radial load applied to the bearings; a portion of the outer peripheral surface of the sleeve that deviates from the support bearings; and an inner peripheral surface of the pulley that disengages from the support bearings. A one-way clutch provided with a one-way clutch that transmits only one-way rotational force provided between the pulley device and the one-way clutch, wherein the one-way clutch is a cam clutch. Pulley device with a built-in one-way clutch.