JP2004347017A - Roller clutch and pulley device with built-in roller clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce friction at a contact part between the rolling surfaces of rollers 10 and a cylindrical surface 13 and friction at a contact part between the rolling surface of rollers 10 and the pressing parts 23 of springs 12a in overrunning. <P>SOLUTION: The springs 12a are formed so that a fixed side half part 24 is disposed in the radial outer direction of a cylindrical space 22 and the pressing parts 23 are acutely bent from the end part of the fixed side half part 24 in the radial inner direction. By this, when the rollers 10 are moved to the radially wide portion of the cylindrical space 22 in the overrunning, the pressing parts 23 are tilted to press the rollers 10 in a direction apart from the cylindrical surface 13. As a result, a contact load on the contact part between the rolling surfaces of the rollers 10 and the cylindrical surface 13 can be reduced. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a pulley device fixed to an end of a rotating shaft of an auxiliary machine for an automobile, such as an alternator which is a generator for an automobile, a compressor, a starter motor, and a pulley used for a rotation transmission unit of various rotary machinery. The present invention relates to improvements in a roller clutch incorporated in a device and a pulley device with a built-in roller clutch that can be used as each of these pulley devices.
[0002]
[Prior art]
2. Description of the Related Art As a pulley device for driving an auxiliary machine such as an alternator for an automobile, a pulley device with a built-in roller clutch is known, for example, as described in Patent Documents 1 and 2. FIGS. 5 and 6 show an example of a pulley device with a built-in roller clutch as a pulley device for driving an alternator, which is conventionally known as described in the above-mentioned patent documents. The roller clutch built-in type pulley device 1 has a sleeve 2 which is an inner diameter side member which can be externally fixed to a rotating shaft of an alternator. A driven pulley 3, which is an outer diameter member, is arranged around the sleeve 2 concentrically with the sleeve 2. A pair of support bearings 4 and 4 and a roller clutch 5 are provided between the outer peripheral surface of the sleeve 2 and the inner peripheral surface of the driven pulley 3.
[0003]
The sleeve 2 is entirely formed in a cylindrical shape, and is fixed to an end of a rotating shaft of the alternator, and is rotatable together with the rotating shaft. For this purpose, in the illustrated example, a screw hole 6 is formed in the middle of the inner peripheral surface of the sleeve 2, and the screw hole 6 and a male screw portion provided on the outer peripheral surface of the tip of the rotating shaft can be screwed freely. And A large-diameter portion 7 having a larger outer diameter than both ends is provided at the center of the outer peripheral surface of the sleeve 2.
[0004]
On the other hand, the outer peripheral surface of the driven pulley 3 has a cross-sectional shape in the width direction as a waveform, and allows a part of an endless belt called a poly-V belt to be freely stretched. The roller clutch 5 is provided at an axially intermediate portion of a space existing between the outer peripheral surface of the sleeve 2 and the inner peripheral surface of the driven pulley 3, and the roller clutch 5 is similarly provided at both axial ends of the space. The support bearings 4 are arranged at positions sandwiched from both sides in the axial direction. The support bearings 4 support the radial load applied to the driven pulley 3 and allow the driven pulley 3 and the sleeve 2 to rotate relative to each other. In the illustrated example, a single row deep groove type ball bearing is used as each of the support bearings 4 and 4.
[0005]
The roller clutch 5 can freely transmit the rotational force between the driven pulley 3 and the sleeve 2 only when the driven pulley 3 tends to rotate relative to the sleeve 2 in a predetermined direction. And Such a roller clutch 5 includes a clutch inner ring 8 which is an inner ring equivalent member, a clutch outer ring 9 which is an outer ring equivalent member, a plurality of rollers 10 and 10, a clutch retainer 11, and a plurality of springs 12. Consisting of The clutch inner ring 8 and the clutch outer ring 9 are formed in a cylindrical shape entirely from a plate material made of hard metal such as bearing steel or carburized steel such as SCM415. The inner ring 8 for the clutch is fixedly fitted to the outer peripheral surface of the large diameter portion 7 of the sleeve 2, and the outer ring 9 for the clutch is fixed to the inner peripheral surface of the intermediate portion of the driven pulley 3 by interference fit. In addition, at least an intermediate portion of the inner peripheral surface of the clutch outer ring 9 that comes into contact with the rollers 10 and 10 is a cylindrical surface 13. At the same time, the outer peripheral surface of the clutch inner ring 8 is a cam surface 14. That is, a plurality of concave portions 15 each called a ramp portion are formed on the outer peripheral surface of the clutch inner ring 8 at equal intervals in the circumferential direction, and the outer peripheral surface of the clutch inner ring 8 is the cam surface 14.
[0006]
In the cylindrical space 22 between the cam surface 14 and the cylindrical surface 13, the clutch retainer 11, the plurality of rollers 10, 10 and the springs 12 are provided. The clutch retainer 11 is made of a synthetic resin (for example, synthetic resin such as polyamide 46 mixed with about 20% of glass fiber) and is integrally formed in a cage-shaped cylindrical shape, and each is annular. The vehicle includes a pair of rim portions 16, 16 and a pillar portion that connects portions of the rim portions 16, 16 near the inner peripheral edge of the inner surface. The clutch retainer 11 is configured such that the projections 17, 17 formed on the inner peripheral surfaces of the rim portions 16, 16 are engaged with the respective recesses 15 forming the cam surface 14, whereby the clutch The relative rotation with respect to the inner ring 8 is disabled. At the same time, a convex portion 18 formed on the inner peripheral surface of the axial end portion (the left end portion in FIG. 5) is provided on the end portion of the large-diameter portion 7 of the sleeve 2 as an outward flange-shaped flange portion 19 formed over the entire circumference. And the inner ring 8 for clutches, whereby positioning in the axial direction is achieved.
[0007]
The rollers 10, 10 are provided in the pockets 20, 20, which are present at a plurality of positions in the circumferential direction of the clutch retainer 11, so that the rollers 10, 10 can be rolled and slightly displaced in the circumferential direction. Further, the same number of the springs 12 as the rollers 10 are locked at a plurality of positions in the circumferential direction of the clutch retainer 11. Each of these springs 12 is formed by bending a stainless steel plate (elastic metal plate) such as SUS304. In a state where the springs 12 are locked to the clutch retainer 11 in this manner, the pressing portions 21 constituting the springs 12 are elastically provided on both sides in the axial direction of the rolling surfaces of the rollers 10, respectively. Contact. The rollers 12 are elastically moved by the springs 12 in the circumferential direction of the cylindrical space 22 between the cylindrical surface 13 and the cam surface 14 so as to be narrow in the radial direction. Pressure. As a result, the switching between the locked state and the overrun state of the roller clutch 5 can be promptly performed during the operation described below.
[0008]
The operation of the roller clutch built-in pulley device 1 configured as described above is as follows. First, the driven pulley 3 to which the clutch outer ring 9 has been fitted and fixed to the sleeve 2 to which the clutch inner ring 8 has been fitted and fixed has a direction in which the springs 12 press the rollers 10 and 10. When rotating in the same direction, a force in the same direction as the pressing direction acts on each of the rollers 10 and 10 from the cylindrical surface 13 and the cam surface 14. As a result, the rollers 10, 10 are displaced toward the radially narrow portion of the cylindrical space 22 and bite into the portion in a wedge shape. As a result, the rotational force can be freely transmitted (locked) between the driven pulley 3 and the sleeve 2, and the two members 2, 3 rotate in synchronization.
[0009]
On the other hand, when the driven pulley 3 rotates in the direction opposite to the pressing direction with respect to the sleeve 2, a force in the direction opposite to the pressing direction is applied to the rollers 10 and 10 from the cylindrical surface 13. Works. As a result, these rollers 10 tend to be displaced toward the radially wide portion of the cylindrical space 22 in the radial direction. At this time, the rollers 10 deflect the pressing portions 21 constituting the springs 12. Then, the rollers 10, 10 displaced toward the wide portion as described above can freely roll at the portion. As a result, transmission of rotational force between the driven pulley 3 and the sleeve 2 becomes impossible (overrun state), and the two members 2 and 3 rotate relative to each other.
[0010]
When the roller clutch 5 is configured as described above, the cylindrical surface 13 and the cam surface 14 that come into contact with the rollers 10 are formed on the inner peripheral surface of the driven pulley 3 and the outer peripheral surface of the sleeve 2, respectively. It may be formed directly. The arrangement of the cylindrical surface 13 and the cam surface 14 in the radial direction may be reversed from the above-described structure, as shown in FIG. That is, the cam surface 14 may be formed on the inner peripheral surface of the clutch outer ring 9a, and the cylindrical surface 13 may be formed on the outer peripheral surface of the clutch inner ring 8a. In this case, when the clutch outer ring 9a rotates in the direction opposite to the pressing direction of the rollers 10 by the springs 12, the lock state is established, and when the clutch outer ring 9a rotates in the same direction as the pressing direction, the overrun state is established.
[0011]
The roller clutch built-in type pulley device 1 configured as described above is fixed to, for example, an end of a rotating shaft of an alternator. The endless belt stretched between the driven pulley 3 and the drive pulley fixed to the end of the crankshaft of the engine and the driven pulley 3 are prevented from rubbing against each other due to the fluctuation of the rotational angular velocity of the crankshaft. I do. As a result, while preventing the endless belt from shortening its life due to the generation of abnormal noise called squeal and abrasion, the rotation speed of the rotating shaft of the alternator rapidly increases even when the rotation speed of the crankshaft decreases rapidly. By preventing the alternator from lowering, it is possible to increase the power generation amount of the alternator. Since these operations have been widely known, detailed descriptions thereof will be omitted.
[0012]
[Patent Document 1]
JP 2002-174270A
[Patent Document 2]
JP-A-2000-240687
[0013]
[Problems to be solved by the invention]
When the roller clutch built-in type pulley device 1 is in the overrun state, the rolling surfaces of the rollers 10 and 10 and the cylindrical surface 13 make sliding contact with each other in a state including rolling contact. On the basis of the friction generated by such sliding contact, the performance of the pulley device 1 with a built-in roller clutch may be reduced at an early stage, or the rotational torque of the pulley device 1 with a built-in roller clutch 1 may increase during overrun. .
[0014]
When the roller clutch built-in type pulley device 1 is incorporated in a device such as a rotation transmitting portion of a copying machine or the like in which the rotation speed of the driven pulley 3 does not increase so much, the rolling surface of each of the rollers 10 and Friction with the cylindrical surface 13 is limited. On the other hand, if the roller clutch built-in type pulley device 1 is incorporated in a device such as an alternator in which the rotational speed of the driven pulley 3 is high, the angular speed fluctuation of the driven pulley 3 is large. The relative angular velocity between the clutch inner ring 8 and the clutch outer ring 9 increases, and the friction between the rolling surfaces of the rollers 10 and the cylindrical surface 13 increases.
[0015]
In particular, as shown in FIGS. 5 and 6, in the case of a structure in which the cam surface 14 is formed on the outer peripheral surface of the inner ring 8 for the clutch and the cylindrical surface 13 is formed on the inner peripheral surface of the outer ring 9 for the clutch, When the centrifugal force acting on each of the rollers 10 and 10 increases as the revolution speed of the rollers 10 and 10 increases, the contact load at the contact portion between the rolling surface of each of the rollers 10 and 10 and the cylindrical surface 13 increases. I do. Then, the friction at the contact portion increases. That is, when the centrifugal force acting on each of the rollers 10, 10 increases, according to the structure shown in FIG. 7, the rollers 10, 10 move toward the bottom of the concave portion 15, and 10 and the cylindrical surface 13 which is the outer peripheral surface of the clutch inner ring 8a tends to separate. On the other hand, in the case of the structure shown in FIGS. 5 and 6, since such an action does not occur, the contact load at the contact portion between each of the rollers 10 and 10 and the cylindrical surface 13 is reduced. 10, the larger the centrifugal force acting on the contact portion, the larger the friction at this contact portion.
[0016]
Further, at the time of overrun, the rollers 10 and 10 rotate on their own due to the friction between the rolling surfaces of the rollers 10 and 10 and the cylindrical surface 13. For this reason, friction at the contact portion between each of the rollers 10 and 10 and the pressing portion 21 of each of the springs 12 pressing the rollers 10 and 10 also poses a problem. In particular, if the contact load between the rolling surface of each of the rollers 10 and 10 and the cylindrical surface 13 is large, the rotation speed of each of the rollers 10 and 10 is increased, and the rotation of each of the rollers 10 and 10 is increased. The friction at the contact portion between the moving surface and the pressing portion 21 of each spring 12 increases.
[0017]
As described above, the contact portions between the rolling surfaces of the rollers 10 and 10 and the cylindrical surface 13 and the contact portions between the rolling surfaces of the rollers 10 and 10 and the pressing portions 21 of the springs 12 are used. Is large, the amount of wear on the rolling surfaces of the rollers 10, 10 and the cylindrical surface 13 and the pressing portion 21 increases, and the performance of the roller clutch built-in pulley device 1 is reduced at an early stage. . In addition, the rotational torque at the time of overrun increases, and the efficiency of various mechanical devices incorporating the roller clutch built-in pulley device 1 deteriorates.
In view of the above-described circumstances, the roller clutch and the roller clutch built-in pulley device of the present invention provide a contact portion between a rolling surface of each roller and a cylindrical surface during overrun, and a rolling surface of each roller. It is invented to reduce the friction at the contact portion between the spring and the pressing portion of the spring.
[0018]
[Means for Solving the Problems]
Among the roller clutch and the pulley device with a built-in roller clutch of the present invention, the roller clutch according to claim 1 includes an outer ring equivalent member, an inner ring equivalent member, a cam surface, a cylindrical surface, a plurality of rollers, and a holding member. A vessel and a plurality of springs.
Of these, the inner ring equivalent member is disposed inside the outer ring equivalent member and concentrically with the outer ring equivalent member.
The cam surface is formed on one of an inner peripheral surface of the outer ring-equivalent member and an outer peripheral surface of the inner ring-equivalent member, and has irregularities in a circumferential direction.
The cylindrical surface is also formed on the other peripheral surface.
The rollers are provided in a cylindrical space between the cam surface and the cylindrical surface.
The retainer is arranged in the cylindrical space so as not to rotate with respect to the member having the cam surface, and retains the rollers so that they can roll and slightly displace in the circumferential direction.
Further, each of the springs is provided between the retainer and each of the rollers, and presses each of the rollers toward a portion where the radial width of the cylindrical space is narrow in the same direction with respect to the circumferential direction. Is what you do.
In particular, in the roller clutch according to the first aspect, each of the springs presses each of the rollers in a direction away from the cylindrical surface at least during overrun.
[0019]
A roller clutch built-in type pulley device according to a second aspect includes an inner diameter side member, an outer diameter side member, a roller clutch, and a support bearing.
The inner diameter side member is fixed to the end of the rotating shaft.
The outer diameter side member is cylindrically arranged around the inner diameter side member, concentrically with the inner diameter side member, and provided with a belt groove on the outer peripheral surface for looping over the belt.
Further, the roller clutch is provided between an outer peripheral surface of the inner diameter side member and an inner peripheral surface of the outer diameter side member, and has a tendency that the outer diameter side member relatively rotates in a predetermined direction with respect to the inner diameter side member. Only when this is the case, the transmission of rotational force between the outer diameter side member and the inner diameter side member can be freely performed.
Further, the support bearing is provided between the outer peripheral surface of the inner diameter side member and the inner peripheral surface of the outer diameter side member at a position adjacent to the roller clutch, and supports a radial load applied to the outer diameter side member. In addition, the relative rotation between the inner diameter side member and the outer diameter side member is made freely.
In particular, in the roller clutch built-in type pulley device described in claim 2, the roller clutch is a roller clutch as described above.
[0020]
[Action]
In the case of the roller clutch and the roller clutch built-in pulley device of the present invention configured as described above, at the time of overrun, each spring presses each roller in a direction away from the cylindrical surface. The contact load at the contact portion between the moving surface and the cylindrical surface can be reduced. Therefore, the friction at the contact portion and at the contact portion between each roller and each spring is reduced to prevent the performance of the roller clutch and the pulley device with a built-in roller clutch from being deteriorated at an early stage. Can be prevented from increasing.
[0021]
BEST MODE FOR CARRYING OUT THE INVENTION
FIG. 1 shows a first example of an embodiment of the present invention. It should be noted that the feature of this example is that in order to reduce the contact load at the contact portion between the rolling surface of each roller 10 and the cylindrical surface 13 at the time of overrun, each roller 12 is attached to each cylindrical surface 13 by each spring 12a. Press in the direction away from the Since the structure and operation of the other parts are the same as those of the conventional structure described above, illustration of the overlapping parts is omitted, and the same reference numerals are given to the same parts in the illustrated parts, and the same parts are overlapped. The description will be omitted or simplified, and the following description focuses on the features of the present invention.
[0022]
This embodiment shows a case where the present invention is applied to a structure in which the cylindrical surface 13 is formed on the inner peripheral surface of the clutch outer race 9 and the cam surface 14 is formed on the outer peripheral surface of the clutch inner race 8. Further, in the case of this example, the clutch retainer (not shown) that holds the rollers 10 is provided with rim portions 16 and 16 in the concave portion 15 that forms the cam surface 14, similarly to the conventional structure shown in FIG. By rotating the protruding pieces 17, 17 (see FIG. 5) formed on the inner peripheral surface of the clutch, the clutch member rotates together with the clutch inner ring 8.
[0023]
In the case of this example, each of the springs 12a is made of stainless steel such as SUS304 (other materials may be used as long as they are conventionally used as a spring of the roller clutch). It is formed by bending a plate material. Then, at the time of overrun, the respective rollers 10 are pressed by the respective springs 12a in a direction away from the cylindrical surface 13 (inward in the radial direction of the cylindrical space 22). That is, each of the springs 12a has a half portion disposed radially outside the cylindrical space 22 to form a fixed side half portion 24 fixed to the clutch retainer, and the other portion bent radially inward. To form a pressing portion 23. Then, the side surface (the left side surface in FIG. 1) of the pressing portion 23 is brought into contact with the rolling surface of each roller 10. The pressing portions 23 are provided at two positions on both ends in the axial direction (front and back directions in FIG. 1) of each of the rollers 10, and the two rollers 10 are positioned at the two positions on both ends in the radial direction of the cylindrical space 22. Is pressed in a narrow direction and in a direction away from the cylindrical surface 13.
[0024]
In the locked state (illustrated state), the pressing portions 23 constituting the respective springs 12a are present at positions shown by solid lines, and the radial width of the cylindrical space 22 is narrow (the direction of the arrow shown by solid lines). Each roller 10 is pressed. On the other hand, at the time of overrun, as shown by the chain line, the roller is pushed by the rollers 10 and tilts in a direction in which the angle formed with the fixed half 24 becomes smaller. Then, with the inclination of the pressing portion 23, each roller 10 is pressed in the direction of the arrow indicated by the chain line. Therefore, at the time of overrun, a force in a direction in which the radial width of the cylindrical space 22 is narrow and a force in a direction away from the cylindrical surface 13 are applied to the rollers 10 from the pressing portion 23. You. The inclination angle of the pressing portion 23 with respect to the locked position (the position indicated by the solid line) increases as the rollers 10 move to the radially wide portion of the cylindrical space 22. Therefore, as the relative rotation speed between the clutch outer ring 9 and the clutch inner ring 8 increases, the more the respective rollers 10 move to the radially wider portion of the cylindrical space 22, the larger the pressing portion. 23 increases the force of pressing these rollers 10 in the direction away from the cylindrical surface 13.
[0025]
In addition, the fixed-side half portion 24 that constitutes each of the springs 12a and that is disposed radially outward of the cylindrical space 22 has sufficient rigidity. Then, it is deformed by the force applied from each of the rollers 10 to prevent a part of the fixed side half 24 from contacting the cylindrical surface 13. On the other hand, the pressing portion 23 which is the remaining portion of each of the springs 12a has a relatively low rigidity in order to change the pressing direction of each of the rollers 10 and to smoothly connect and disconnect the roller clutch as described above. It cannot be higher. Therefore, in the case of the present example, the springs 12a are formed such that the plate thickness of the fixed side half 24 is thick (or wide) and the plate thickness of the pressing portion 23 is thin (or narrow). Thus, the rigidity of the pressing portion 23 and the rigidity of the fixed half portion 24 are different.
[0026]
In the case of this example having the above-described configuration, the pressing portion 23 forming each of the springs 12a presses each of the rollers 10 in a direction away from the cylindrical surface 13 during overrun. The contact load at the contact portion between the rolling surface 10 and the cylindrical surface 13 can be reduced. Therefore, even if the centrifugal force acting on each of the rollers 10 increases as the revolution speed of each of the rollers 10 increases, each of the rollers 10 is pressed by the pressing portion 23 in a direction away from the cylindrical surface 13. Thus, the friction at the contact portion can be reduced. Also, the rotation speed of each roller 10 is prevented from increasing, and the friction at the contact portion between the rolling surface of each roller 10 and the pressing portion 23 of each spring 12a can be reduced. Then, by reducing the amount of wear at each of these contact portions, it is possible to prevent the performance of the roller clutch and the pulley device with a built-in roller clutch from being deteriorated at an early stage, and to prevent an increase in the rotational torque at the time of overrun.
[0027]
Next, FIG. 2 shows a second example of the embodiment of the present invention. Also in the case of this example, the present invention is applied to a structure in which a cylindrical surface 13 is formed on the inner peripheral surface of the clutch outer race 9 and a cam surface 14 is formed on the outer peripheral surface of the clutch inner race 8. In the case of this example, in order to press each roller 10 in the direction away from the cylindrical surface 13 by each spring 12b at the time of overrun, each spring 12b has the following shape. That is, the pressing portion 25 constituting each of the springs 12b is inclined in a direction toward the radially outward as the radial width of the cylindrical space 22 decreases. The pressing portion 25 is brought into contact with the rolling surface of each roller 10 on the outer side in the radial direction of the cylindrical space 22. As a result, each of the rollers 10 is pressed by the pressing portion 25 in a direction toward the narrow portion of the cylindrical space 22 in the radial direction and in a direction away from the cylindrical surface 13. Other structures and operations are almost the same as those in the first example.
[0028]
Next, FIG. 3 shows a third example of the embodiment of the present invention. This example shows a case where the present invention is applied to a structure in which a cylindrical surface 13 is formed on the outer peripheral surface of the clutch inner ring 8a and a cam surface 14 is formed on the inner peripheral surface of the clutch outer ring 9a. In the case of this example having such a structure, the cam surface 14 exists outside the cylindrical space 22 in the radial direction. In the overrun state, each roller 10 held by a clutch retainer (not shown) that rotates together with the clutch outer ring 9a relatively rotates with the clutch inner ring 8a. The rolling surfaces of the rollers 10 and the cylindrical surface 13 formed on the outer peripheral surface of the clutch inner ring 8a make sliding contact with each other in a state including rolling contact.
[0029]
Therefore, in the case of this example, at the time of overrun, the respective rollers 10 are pressed radially outward of the cylindrical space 22 by the respective springs 12c. For this purpose, each of the springs 12c is installed so as to be opposite in the radial direction of the cylindrical space 22 from the case of the first example described above. That is, the fixed half 24a is arranged radially inside the cylindrical space 22, and the remaining pressing portion 23a is bent radially outward from the end of the fixed half 24a. The other structure of each spring 12c is the same as that of each spring 12a of the first example.
[0030]
In the case of the present embodiment configured as described above, as the rollers 10 move to a portion where the radial width of the cylindrical space 22 is large in the overrun, the pressing portion 23a The force of pressing outward in the radial direction of the cylindrical space 22, that is, in the direction away from the cylindrical surface 13, increases. Therefore, the contact load at the contact portion between the rolling surface of each roller 10 and the cylindrical surface 13 is reduced, and the contact portion, the rolling surface of each roller 10 and the pressing portion 23a of each spring 12c are reduced. Friction at the contact portion with the contact can be reduced. In the case of this example, when the centrifugal force acting on each of the rollers 10 increases, each of the rollers 10 is displaced to a deep portion of the recess 15 while elastically deforming the pressing portion 23a. Therefore, even if the centrifugal force increases, the contact load at the contact portion between each roller 10 and the cylindrical surface 13 does not increase. Therefore, although the structure of this embodiment does not achieve the effects of the first and second embodiments described above, it is applied to, for example, a device in which the rotation speed of the pulley does not increase so much to improve the service life of this device and increase the overrun. The rotational torque at the time can be reduced.
[0031]
Next, FIG. 4 shows a fourth example of the embodiment of the present invention. Also in the case of the present example, the present invention is applied to a structure in which a cylindrical surface 13 is formed on the outer peripheral surface of the clutch inner ring 8a and a cam surface 14 is formed on the inner peripheral surface of the clutch outer ring 9a, as in the third example described above. Have applied. For this reason, in the case of this example, each spring 12d is installed so as to be opposite in the radial direction of the cylindrical space 22 from the case of the above-described second example. In other words, the pressing portion 25a constituting each of the springs 12d is inclined in a direction inward in the radial direction as the radial width of the cylindrical space 22 decreases. The pressing portion 25a is in contact with the rolling surface of each of the rollers 10 on the inner side in the radial direction of the cylindrical space 22. As a result, each of the rollers 10 is pressed by the pressing portion 25 a in a direction toward the narrow portion of the cylindrical space 22 in the radial direction and in a direction away from the cylindrical surface 13. Other structures and operations are the same as those of the third example described above.
[0032]
【The invention's effect】
Since the present invention is constructed and operated as described above, the reliability and durability of the roller clutch and the roller clutch built-in pulley device can be improved, and the roller clutch or the roller clutch built-in pulley device is incorporated. The efficiency of various mechanical devices can be improved.
[Brief description of the drawings]
FIG. 1 is a view similar to FIG. 6, showing a first example of an embodiment of the present invention;
FIG. 2 is a view similar to FIG. 1, showing the second example;
FIG. 3 is a view similar to FIG. 1, showing the third example;
FIG. 4 is a view similar to FIG. 1, showing the fourth example;
FIG. 5 is a sectional view showing an example of a conventional structure.
FIG. 6 is a sectional view taken along line AA of FIG. 5, showing only a roller clutch taken out.
FIG. 7 is a view similar to FIG. 6, showing another example of the roller clutch.
[Explanation of symbols]
Reference Signs List 1 Pulley device with built-in roller clutch 2 Sleeve 3 Driven pulley 4 Support bearing 5, 5a Roller clutch 6 Screw hole 7 Large diameter portion 8, 8a Inner ring for clutch 9, 9a Outer ring for clutch 10 Roller 11 Retainer for clutch 12, 12a , 12b, 12c, 12d Spring 13 Cylindrical surface 14 Cam surface 15 Recess 16 Rim 17 Projection 18 Convex 19 Flange 20 Pocket 21 Pressing portion 22 Cylindrical space 23, 23a Pressing portion 24, 24a Fixed side half 25, 25a Pressing part

Claims (2)

An outer ring equivalent member, an inner ring equivalent member disposed concentrically with the outer ring equivalent member inside the outer ring equivalent member, and one of an inner peripheral surface of the outer ring equivalent member and an outer peripheral surface of the inner ring equivalent member A cam surface formed in the circumferential direction, a cylindrical surface formed on the other circumferential surface, and a plurality of cam surfaces provided in a cylindrical space between the cam surface and the cylindrical surface. And a retainer which is arranged in the cylindrical space so as to be unable to rotate with respect to the member forming the cam surface, and which holds the rollers so that they can roll and slightly displace in the circumferential direction. A roller clutch provided between the retainer and each of the rollers, and a plurality of springs that press each of the rollers toward a narrow portion of the cylindrical space in the radial direction and press in the same direction with respect to the circumferential direction. In each of these springs At least during overrun roller clutch of the rollers, characterized in that it is pressed in the direction away from said cylindrical surface. An inner diameter side member fixed to the end of the rotating shaft, and a cylindrical outer diameter side which is arranged around the inner diameter side member concentrically with the inner diameter side member and provided with a belt groove for passing a belt around the outer peripheral surface. Member, provided between the outer peripheral surface of the inner diameter side 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 roller clutch for freely transmitting a rotational force between the outer diameter side member and the inner diameter side member, and an outer circumferential surface of the inner diameter side member and an inner circumference of the outer diameter side member at a position adjacent to the roller clutch. A pulley device with a built-in roller clutch, comprising a support bearing provided between the inner surface and the outer surface to support the radial load applied to the outer diameter member while allowing relative rotation between the inner diameter member and the outer diameter member. The roller clutch according to claim 1, wherein It characterized that it is placing the roller clutch, the roller clutch built-in type pulley apparatus.

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