JP4239682B2 - Roller clutch and roller clutch built-in pulley device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pulley device that is fixed to an end of a rotating shaft of an alternator that is a generator for an automobile, or an auxiliary machine for an automobile such as a compressor and a starter motor, and a pulley that is used for a rotation transmission part of various rotary machine devices The present invention relates to an improvement in a roller clutch incorporated in the apparatus and a roller clutch built-in type pulley apparatus that can be used as each pulley apparatus.
[0002]
[Prior art]
As a pulley apparatus for driving an auxiliary machine such as an alternator for an automobile, a pulley apparatus with a built-in roller clutch is known as described in Patent Documents 1 and 2, for example. 3 to 4 show an example of a pulley device with a built-in roller clutch that has been conventionally known as a pulley device for driving an alternator, as described in the above-mentioned patent documents. This pulley device 1 with a built-in roller clutch has a sleeve 2 that is an inner diameter side member that can be fitted and fixed to the rotating shaft of the alternator. A driven pulley 3 that is an outer diameter side member is disposed concentrically with the sleeve 2 around 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 formed in a cylindrical shape as a whole, is fixed to the end of the rotating shaft of the alternator, and is rotatable with the rotating shaft. Therefore, in the illustrated example, a screw hole portion 6 is formed in the middle portion of the inner peripheral surface of the sleeve 2, and the screw hole portion 6 and a male screw portion provided on the outer peripheral surface of the tip end portion of the rotating shaft can be screwed together. It is said. A large-diameter portion 7 having a larger outer diameter than both ends is also provided at the center of the outer peripheral surface of the sleeve 2.
[0004]
On the other hand, on the outer peripheral surface of the driven pulley 3, a part of an endless belt called a poly-V belt can be passed around with a cross-sectional shape in the width direction as a waveform. Then, the roller clutch 5 is disposed at the axially intermediate portion of the 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 disposed at both axial end portions of the space. The support bearings 4 and 4 are arranged at positions sandwiched from both sides in the axial direction. Of these, the support bearings 4, 4 support a radial load applied to the driven pulley 3, while allowing relative rotation between the driven pulley 3 and the sleeve 2. 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 that is an inner ring equivalent member, a clutch outer ring 9 that is an outer ring equivalent member, a plurality of rollers 10 and 10, a clutch retainer 11, and a plurality of springs 12. It consists of. Of these, the inner ring for clutch 8 and the outer ring for clutch 9 are each formed in a cylindrical shape by a plate made of hard metal such as bearing steel or carburized steel such as SCM415. The clutch inner ring 8 is fitted and fixed to the outer peripheral surface of the large-diameter portion 7 of the sleeve 2 and the clutch outer ring 9 is fixed to the inner peripheral surface of the intermediate portion of the driven pulley 3 by an interference fit. Of the inner peripheral surface of the clutch outer ring 9, at least an intermediate portion that contacts 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 used as a cam surface 14. That is, a plurality of recesses 15 called ramp portions are formed at equal intervals in the circumferential direction on the outer peripheral surface of the clutch inner ring 8, and the outer peripheral surface of the clutch inner ring 8 is used as 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 spring 12 are provided. Of these, the clutch retainer 11 is integrally formed in a bowl-shaped cylindrical shape with a synthetic resin (for example, a synthetic resin such as polyamide 46 mixed with about 20% of glass fiber), and each is annular. A pair of rim portions 16, 16 and a column portion connecting the inner rim portions of the rim portions 16, 16 are provided. Such a clutch retainer 11 is formed by engaging the projecting pieces 17, 17 formed on the inner peripheral surfaces of the rim parts 16, 16 with the recesses 15 constituting the cam surface 14. The relative rotation with respect to the inner ring 8 is disabled. At the same time, an outward flange-like flange portion 19 is formed on the end portion of the large-diameter portion 7 of the sleeve 2 over the entire circumference with a convex portion 18 formed on the inner peripheral surface of the axial end portion (left end portion in FIG. 3 ) . And the clutch inner ring 8 to achieve positioning in the axial direction.
[0007]
Further, in the pockets 20, 20 existing at a plurality of locations in the circumferential direction of the clutch retainer 11, the rollers 10, 10 are provided so as to be able to roll and slightly displace in the circumferential direction. Further, the same number of the respective springs 12 as the respective rollers 10 and 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 material (elastic metal plate) such as SUS304. Thus, in a state where the springs 12 are locked to the clutch retainer 11, the pressing portions 21 constituting the springs 12 are elastically formed on both axial sides of the rolling surfaces of the rollers 10 and 10, respectively. Abut. The respective springs 10 and 10 are elastically moved in the same direction with respect to the circumferential direction by the springs 12 toward the narrower portion of the cylindrical space 22 between the cylindrical surface 13 and the cam surface 14 in the radial direction. Press. As a result, during the operation described later, the roller clutch 5 can be quickly switched between the locked state and the overrun state.
[0008]
The operation of the roller clutch built-in pulley apparatus 1 configured as described above is as follows. First, the driven pulley 3 having the clutch outer ring 9 fitted and fixed to the sleeve 2 to which the clutch inner ring 8 is fitted and fixed has a pressing direction of the rollers 10 and 10 by the springs 12. When rotating in the same direction, a force in the same direction as the pressing direction acts on the rollers 10 and 10 from the cylindrical surface 13 and the cam surface 14. As a result, each of the rollers 10 and 10 is displaced toward a narrow portion in the radial direction of the cylindrical space 22 and bites into the portion in a wedge shape. As a result, rotational force can be freely transmitted between the driven pulley 3 and the sleeve 2 (locked state), and both the members 2 and 3 rotate in synchronization.
[0009]
On the other hand, when the driven pulley 3 rotates with respect to the sleeve 2 in the direction opposite to the pressing direction, a force in the direction opposite to the pressing direction is applied from the cylindrical surface 13 to the rollers 10 and 10. Works. As a result, each of the rollers 10 and 10 tends to be displaced toward a wide portion in the radial direction of the cylindrical space 22. At this time, the rollers 10, 10 bend the pressing portions 21 constituting the springs 12. And each roller 10 and 10 displaced toward the wide part as mentioned above becomes free to roll in the said part. As a result, the rotational force cannot be transmitted between the driven pulley 3 and the sleeve 2 ( overrun state), and both the members 2 and 3 rotate relative to each other.
[0010]
In the case of constituting the roller clutch 5 as described above, the cylindrical surface 13 and the cam surface 14 that are in contact with the rollers 10 and 10 are respectively connected to the inner peripheral surface of the driven pulley 3 and the outer peripheral surface of the sleeve 2. It may be formed directly. Further, 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, the clutch outer ring 9a is in a locked state when rotating in the direction opposite to the pressing direction of each roller 10 by each spring 12, and is in an overrun state when rotating in the same direction as this pressing direction.
[0011]
The roller clutch built-in pulley device 1 configured as described above is fixed to, for example, an end portion of a rotating shaft of an alternator. Then, the endless belt stretched between the driven pulley 3 and the driving pulley fixed to the end of the engine crankshaft and the driven pulley 3 are prevented from rubbing due to fluctuations in the rotational angular velocity of the crankshaft. To do. As a result, it is possible to prevent the endless belt from being shortened due to the occurrence of abnormal noise called squealing or wear, and when the rotational speed of the crankshaft is drastically reduced, the rotational speed of the rotating shaft of the alternator is sharply It is possible to prevent the decrease and increase the power generation amount of this alternator. Since these actions have been widely known, detailed description thereof will be omitted.
[0012]
[Patent Document 1]
JP2002-174270
[Patent Document 2]
JP2000-240687
[0013]
[Problems to be solved by the invention]
When the roller clutch built-in pulley apparatus 1 is in an overrun state, the rolling surfaces of the rollers 10 and 10 and the cylindrical surface 13 are in sliding contact with each other including rolling contact. Based on the friction generated by such sliding contact, the performance of the pulley apparatus 1 with a built-in roller clutch may be deteriorated early, or the rotational torque at the time of overrun of the pulley apparatus 1 with a built-in roller clutch may increase. .
[0014]
When the pulley device 1 with a built-in roller clutch is incorporated in a device in which the rotational speed of the driven pulley 3 does not increase so much, such as a rotation transmission unit of a copying machine or the like, the rolling surfaces of the rollers 10 and 10 Friction with the cylindrical surface 13 is limited. On the other hand, when the pulley device 1 with a built-in roller clutch is incorporated in a device such as an alternator in which the rotational speed of the driven pulley 3 is high, the variation in the angular velocity 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 10 and the cylindrical surface 13 increases.
[0015]
In particular, as shown in FIGS. 3 to 4 , in the structure in which the cam surface 14 is formed on the outer peripheral surface of the clutch inner ring 8 and the cylindrical surface 13 is formed on the inner peripheral surface of the clutch outer ring 9, each of the rollers 10. When the centrifugal force acting on these rollers 10 and 10 increases as the revolution speed of 10 increases, the contact load at the contact portion between the rolling surfaces of these rollers 10 and 10 and the cylindrical surface 13 increases. To do. And the friction in this contact part becomes large. That is, when the centrifugal force acting on each of these rollers 10 and 10 increases, according to the structure shown in FIG. 5 described above, each of the rollers 10 and 10 moves toward the bottom of the recess 15 and each of these rollers 10 10 rolling surfaces and the cylindrical surface 13 which is the outer peripheral surface of the clutch inner ring 8a tend to be separated from each other. On the other hand, in the case of the structure shown in FIGS. 3 to 4 , such an action does not occur. 10 increases as the centrifugal force acting on 10 increases, and the friction at this contact portion also increases.
[0016]
Further, during overrun, the rollers 10 and 10 rotate due to friction between the rolling surfaces of the rollers 10 and 10 and the cylindrical surface 13. For this reason, the friction at the contact portion between the rollers 10 and 10 and the pressing portion 21 of the spring 12 that presses the rollers 10 and 10 also becomes a problem. In particular, when the contact load at the contact portion 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 increases, and the rotation of these rollers 10 and 10 increases. Friction at the contact portion between the moving surface and the pressing portion 21 of each spring 12 increases.
[0017]
As described above, at the contact portion between the rolling surface of each roller 10, 10 and the cylindrical surface 13, and the contact portion between the rolling surface of each roller 10, 10 and the pressing portion 21 of each spring 12. When the friction 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 quickly reduced. . Moreover, the rotational torque at the time of overrun increases, and the efficiency of various mechanical devices incorporating this roller clutch built-in pulley device 1 is deteriorated.
In view of the circumstances as described above, the roller clutch and the pulley device with a built-in roller clutch of the present invention are in contact with the rolling surface of each roller and the cylindrical surface, and the rolling surface of each roller during overrun. 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]
Of the roller clutch and the roller clutch built-in type pulley device of the present invention, the roller clutch described in 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. 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 peripheral surface of the inner peripheral surface of the outer ring equivalent member and the outer peripheral surface of the inner ring equivalent member, and is uneven in the circumferential direction.
The cylindrical surface is also formed on the other peripheral surface.
Each of the rollers is provided in a cylindrical space between the cam surface and the cylindrical surface.
The cage is disposed in the cylindrical space so as not to rotate with respect to the member having the cam surface, and holds the rollers so as to be able to roll and slightly displace in the circumferential direction.
Each of the springs is provided between the retainer and the rollers, and presses the rollers in the same direction with respect to the circumferential direction toward the narrow radial portion of the cylindrical space. To do.
In particular, in the roller clutch according to claim 1, each of the springs presses the rollers in a direction away from the cylindrical surface, and the rollers press the force in this direction. In order to increase the width of the space in the radial direction, the respective springs are fixed to the retainer, and the cam is connected to the radial direction of the cylindrical space from the end of the fixed portion. It comprises a pressing part that is bent toward the surface side and presses each of the rollers, and a bent part that continues the pressing part and the fixing part. Of these, the bent portion is positioned closer to the cylindrical surface than the center of each roller with respect to the radial direction of the cylindrical space, and the circular portion of the cylindrical space increases toward the tip side. It is made to incline in the direction away from each said roller regarding the circumferential direction .
[0019]
A pulley apparatus with a built-in roller clutch according to a second aspect includes an inner diameter side member, an outer diameter side member, a roller clutch, and a support bearing.
Of these, the inner diameter side member is fixed to the end of the rotating shaft.
The outer diameter side member is a cylindrical member that is arranged concentrically with the inner diameter side member around the inner diameter side member, and is provided with a belt groove for passing the belt around the outer peripheral surface.
The roller clutch is provided between the outer peripheral surface of the inner diameter side member and the inner peripheral surface of the outer diameter side member, and the outer diameter side member tends to rotate relative to the inner diameter side member in a predetermined direction. Only in this case, rotational force can be freely transmitted between the outer diameter side member and the inner diameter side member.
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. However, relative rotation between the inner diameter side member and the outer diameter side member can be freely performed.
In particular, in the pulley apparatus with a built-in roller clutch described in claim 2, the roller clutch is a roller clutch as described in claim 1 above.
[0020]
[Action]
In the case of the roller clutch and the roller clutch built-in type pulley device of the present invention configured as described above, during 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. In particular, in the case of the present invention, as the relative rotational speed between the outer ring equivalent member and the inner ring equivalent member increases, the rollers move to the portion where the radial width of the cylindrical space is wider. Can be increased in the direction away from the cylindrical surface. Therefore, by reducing the friction at the contact portion between the contact portion and the respective rollers and each spring, the performance of the roller clutch and roller clutch built-in type pulley apparatus while preventing a decrease in the early, during overrun An increase in rotational torque can be prevented.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 shows a first example of an embodiment of the present invention. The feature of this example is that, in the event of overrun, in order to reduce the contact load at the contact portion between the rolling surface of each roller 10 and the cylindrical surface 13, each roller 10 is connected to this cylindrical surface 13 by each spring 12a. It is in the point which pushes in the direction away from. Since the structure and operation of the other parts are the same as in the case of the conventional structure described above, the illustration of the overlapping parts is omitted, and the same parts are denoted by the same reference numerals in the illustrated parts, and are duplicated. The description will be omitted or simplified, and the following description will focus on the features of the present invention.
[0022]
This example 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 ring 9 and the cam surface 14 is formed on the outer peripheral surface of the clutch inner ring 8. In the case of this example, a clutch retainer (not shown) that holds the rollers 10 is provided with rim portions 16 and 16 in a recess 15 that constitutes the cam surface 14 as in the conventional structure shown in FIG. Rotate together with the clutch inner ring 8 by engaging projecting pieces 17, 17 (see FIG. 3 ) formed on the inner peripheral surface of the clutch.
[0023]
In the case of this example, each of the springs 12a is made of stainless steel such as SUS304 (other materials are applicable as long as they are conventionally used as springs for roller clutches). It is formed by bending a plate material. At the time of overrun, the respective springs 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 is arranged on the outer side in the radial direction of the cylindrical space 22 and fixed to the clutch retainer 24 (corresponding to the fixed portion described in the claims). The remaining portion is bent radially inward from the bent portion 26 to form the pressing portion 23. The side surface (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 of each roller 10 in the axial direction (front and back direction in FIG. 1). The rollers 10 are disposed at two positions on both ends, and the width of the cylindrical space 22 in the radial direction. Is pressed in a narrow direction and away from the cylindrical surface 13. Further, in the case of this example, by arranging the bent portion 26 in the radially outward portion of the cylindrical space 22, the radial direction of the cylindrical space 22 is determined from the center O of each roller 10. Is also located on the cylindrical surface 13 side.
[0024]
In the locked state (shown state), the pressing portion 23 constituting each spring 12a is present at the position indicated by the solid line, and the radial width of the cylindrical space 22 is narrow (the direction of the arrow indicated by the solid line). Each of the rollers 10 is pressed. On the other hand, at the time of overrun, as shown by a chain line, the roller 10 is pushed by each of the rollers 10 and is inclined in a direction in which an angle formed with the fixed-side half portion 24 is reduced. Specifically, the pressing portion 23 is inclined more greatly in the direction away from the rollers 10 with respect to the circumferential direction of the cylindrical space 22 toward the distal end side. Then, with the inclination of the pressing portion 23 as described above, each roller 10 is pressed in the direction of the arrow indicated by the chain line. Accordingly, at the time of overrun, the force from the pressing portion 23 toward the rollers 10 toward the direction in which the radial width of the cylindrical space 22 is narrow and the direction away from the cylindrical surface 13 (inward in the radial direction) . Power is granted. Further, 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 a portion where the radial width of the cylindrical space 22 is wide. For this reason, as the relative rotational speed between the outer ring for clutch 9 and the inner ring for clutch 8 increases, the pressing portion increases as the rollers 10 move to a portion where the radial width of the cylindrical space 22 is wider. 23 increases the force for pressing these rollers 10 away from the cylindrical surface 13.
[0025]
In addition, the said fixed side half part 24 which comprises the said each spring 12a arrange | positioned in the radial direction outer side of the said cylindrical space 22 ensures sufficient rigidity. And it deform | transforms with the force which acts from each said roller 10, and prevents that a part of this fixed side half part 24 contacts the said cylindrical surface 13. FIG. On the other hand, the pressing portion 23 which is the remaining portion of each spring 12a changes the direction in which the rollers 10 are pressed as described above, or smoothly connects and disconnects the roller clutch. Can't be high. Therefore, in the case of this example, each spring 12a is formed so that the plate thickness of the fixed half portion 24 is thick (or wide) and the plate of the pressing portion 23 is thin (or narrow). Thus, the rigidity of the pressing portion 23 and the rigidity of the stationary half portion 24 are different.
[0026]
In the case of this example configured as described above, the pressing portion 23 configuring each spring 12a presses each roller 10 in a direction away from the cylindrical surface 13 during overrun. The contact load at the contact portion between the ten rolling surfaces and the cylindrical surface 13 can be reduced. For this reason, even if the centrifugal force acting on each roller 10 increases as the revolution speed of each roller 10 increases, the pressing portion 23 presses each roller 10 in the direction away from the cylindrical surface 13. Thus, friction at the contact portion can be reduced. Further, 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. In addition, the amount of wear at each contact portion can be reduced to prevent the performance of the roller clutch and the roller clutch built-in pulley apparatus from deteriorating at an early stage, and to prevent an increase in rotational torque during overrun.
[0027]
Next, FIG. 2 shows a second 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 on the radially outer side of the cylindrical space 22. In the overrun state, each roller 10 that rotates together with the clutch outer ring 9a and that is held by a clutch retainer (not shown) rotates relative to the clutch inner ring 8a. The rolling surfaces of these rollers 10 and the cylindrical surface 13 formed on the outer peripheral surface of the clutch inner ring 8a are in sliding contact with each other in a state including rolling contact.
[0028]
Therefore, in this example, at the time of overrun, the rollers 10 are pressed outward in the radial direction of the cylindrical space 22 by the springs 12c. For this purpose, each of the springs 12c is installed so as to be reversed with respect to the radial direction of the cylindrical space 22 in the case of the first example described above. That is, the fixed-side half 24a is disposed radially inward of the cylindrical space 22, and the remaining pressing portion 23a is radially outward from the end of the fixed-side half 24a starting from the bent portion 26a. Is bent. In addition, the other structure of each said spring 12c is the same as that of each spring 12a of the said 1st example.
[0029]
In the case of the present example configured as described above, the pressing portion 23a causes the rollers 10 to move to the portions where the radial width of the cylindrical space 22 is wider at the time of overrun. 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. For this reason, 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. Friction at the contact portion with can be reduced. In the case of this example, when the centrifugal force acting on each roller 10 increases, each roller 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, the structure of this example does not provide the same effect as the first example described above. However, for example, the structure of this example is applied to a device in which the rotational speed of the pulley does not increase so much. Reduction of rotational torque can be achieved.
[0030]
【The invention's effect】
Since the present invention is configured and operates as described above, it is possible to improve the reliability and durability of the roller clutch and the pulley device with a built-in roller clutch, and incorporate the roller clutch or the pulley device with a built-in roller clutch. However, the efficiency of various mechanical devices can be improved.
[Brief description of the drawings]
FIG. 1 is a view similar to FIG. 4 , 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 cross-sectional view showing an example of a conventional structure.
4 is a cross-sectional view taken along the line AA in FIG. 3, showing only the roller clutch removed.
FIG. 5 is a view similar to FIG. 4 showing another example of the roller clutch.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Roller clutch built-in pulley apparatus 2 Sleeve 3 Driven pulley 4 Support bearing 5, 5a Roller clutch 6 Screw hole part 7 Large diameter part 8, 8a Clutch inner ring 9, 9a Clutch outer ring 10 Roller 11 Clutch retainer 12, 12a 12c spring 13 cylindrical surface 14 cam surface 15 concave portion 16 rim portion 17 projecting piece 18 convex portion 19 collar portion 20 pocket 21 pressing portion 22 cylindrical space 23, 23a pressing portion 24, 24a fixed side half
26, 26a Bent part

Claims (2)

One outer surface of 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 an inner peripheral surface of the outer ring equivalent member and an outer peripheral surface of the inner ring equivalent member And a cam surface that is uneven in the circumferential direction, a cylindrical surface that is also formed on the other peripheral surface, and a plurality of cam surfaces provided in the cylindrical space between the cam surface and the cylindrical surface And a cage that is disposed in the cylindrical space so as not to rotate with respect to the member forming the cam surface, and holds each of the rollers so as to roll and slightly displace in the circumferential direction. A roller clutch comprising a plurality of springs provided between the cage and each of the rollers and pressing each of the rollers toward the narrow radial portion of the cylindrical space in the same direction with respect to the circumferential direction. in, in each of these springs Ri, the respective rollers as well as pressed in the direction away from said cylindrical surface, to a force pressing to the direction of these respective rollers large enough to move to the wide portion in the radial direction of the cylindrical space, each A spring that is fixed to the cage; a pressing portion that is bent toward the cam surface with respect to the radial direction of the cylindrical space from the end of the fixing portion; It comprises a bent part that continues the pressing part and the fixed part, of which the bent part is positioned closer to the cylindrical surface than the center of each roller in the radial direction of the cylindrical space, and the pressing part The roller clutch is characterized by being inclined in a direction away from each of the rollers with respect to the circumferential direction of the cylindrical space toward the tip side .   A cylindrical outer diameter side member that is fixed to the end of the rotating shaft, and that is provided concentrically with the inner diameter side member around the inner diameter side member and provided with a belt groove over the outer peripheral surface for belt belting. Only when the member is provided between the outer peripheral surface of the inner diameter side member and the inner peripheral surface of the outer diameter side member, and the outer diameter side member tends to rotate relative to the inner diameter side member in a predetermined direction, A roller clutch that allows transmission of rotational force between the outer diameter side member and the inner diameter side member, and an outer peripheral surface of the inner diameter side member and an inner periphery of the outer diameter side member at a position adjacent to the roller clutch. Roller clutch built-in type pulley device provided with a support bearing provided between the inner surface and the outer diameter side member so as to allow relative rotation between the inner diameter side member and the outer diameter side member while supporting a radial load applied to the outer diameter side member The roller clutch according to claim 1. It characterized that it is placing the roller clutch, the roller clutch built-in type pulley apparatus.

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