JP2005036907A - Roller clutch and pulley device with built-in roller clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a roller clutch 5a from lowering in the durability and from malfunctioning by directly bringing each spring 11a, 11a into contact with each roller 10, 10. <P>SOLUTION: The roller clutch locks each spring 11a, 11a in projections 24, 24 formed in the periphery of an inner ring 9a, respectively. Each roller 10, 10 is pressed via a retainer 12a with each spring 11a, 11a. This makes it possible to prevent each spring 11a, 11a from getting into contact with each roller 10, 10. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a roller clutch incorporated in a pulley for use in an auxiliary machine such as an alternator, which is a generator of an automobile, a crank pulley, a compressor, etc., and an improvement in a pulley device incorporating a roller clutch used as such a pulley. About.

  2. Description of the Related Art A pulley device with a built-in roller clutch in which a roller clutch is incorporated in a pulley device of an automobile auxiliary machine such as an alternator has been conventionally known as described in Patent Documents 1 to 3, for example. 4 to 6 show an example of a pulley device with a built-in roller clutch, which is conventionally known as described in each of these patent documents. The pulley apparatus 1 with a built-in roller clutch is for fixing the endless belt to the outer peripheral surface of the pulley element 2 which is an outer diameter side member described in the claims, and the tip of a rotary drive shaft such as an alternator. The sleeve 3 which is the inner diameter side member described in the claims is arranged concentrically with each other.

  Further, between the outer peripheral surface of the sleeve 3 and the inner peripheral surface of the pulley element 2, deep groove type ball bearings 4, 4 and a roller clutch 5, each being a support bearing, are provided. In order to provide the ball bearings 4 and 4 and the roller clutch 5, the inner peripheral surface of the pulley element 2 is a simple cylindrical surface, and the outer peripheral surface of the sleeve 3 is formed between the large-diameter portion 6 at the axial intermediate portion and the both end portions. A stepped cylindrical surface in which the small-diameter portions 7 and 7 are continuously provided at the stepped portion is used.

  Then, the roller clutch 5 is disposed at the axially intermediate portion of the annular space existing between the outer peripheral surface of the sleeve 3 and the inner peripheral surface of the pulley element 2, and the roller clutch is disposed at both axially adjacent portions of the annular space. The ball bearings 4 and 4 are arranged at positions sandwiching 5 from both sides in the axial direction. Of these, the ball bearings 4 and 4 have the role of allowing the pulley element 2 and the sleeve 3 to be concentrically arranged and allowing the relative rotation of the members 2 and 3 to be freely made. In the illustrated example, by installing the ball bearings 4 and 4 on both sides of the roller clutch 5, a span for applying a radial load is lengthened to increase rigidity and ensure durability.

  The roller clutch 5 includes an outer ring 8 that is an outer ring equivalent member, an inner ring 9 that is an inner ring equivalent member, a plurality of rollers 10 and 10, and the same number of springs 11 and 11 as the rollers 10 and 10, and a cage. Twelve. The inner ring 9 is formed of a steel material in a cylindrical shape, and has an outer peripheral surface provided with a cam surface 13 that is uneven in the circumferential direction. That is, the outer peripheral surface of the inner ring 9 is formed as a cam surface 13 by forming a plurality of concave portions 14 and 14 called ramp portions at equal intervals in the circumferential direction on the outer peripheral surface of the inner ring 9. The outer ring 8 is made of steel, and the inner peripheral surface is a cylindrical surface 15. The inner ring 9 is disposed concentrically with the outer ring 8 inside the outer ring 8. Between the cam surface 13 provided on the outer peripheral surface of the inner ring 9 and the cylindrical surface 15 provided on the inner peripheral surface of the outer ring 8, the rollers 10, 10, the springs 11, 11, and the holding member are provided. A container 12 is arranged.

  Of these, the cage 12 is formed in a vertical cylindrical shape by injection molding a synthetic resin (for example, a thermoplastic resin such as polyamide 46 mixed with about 20% glass fiber). Such a cage 12 is related to the circumferential direction in a state in which a pair of rim portions 16, 16 each having an annular shape and the radially inner ends of the inner side surfaces of the rim portions 16, 16 are connected to each other. And a plurality of connecting portions 17 and 17 arranged at equal intervals. Such a retainer 12 is formed by engaging the protrusions 18 and 18 formed on the inner peripheral surfaces of the rim portions 16 and 16 with the recesses 14 and 14 constituting the cam surface 13. The relative rotation with respect to 9 is disabled. Further, support plate portions 19 and 19 are formed on the outer peripheral surfaces of the connecting portions 17 and 17 so as to protrude radially outward. Portions surrounded by the rim portions 16 and 16 and the support plate portions 19 and 19 that are adjacent to each other in the circumferential direction are pockets 20 and 20, respectively. 10 is provided so as to be slightly displaceable in the rolling and circumferential directions.

  The springs 11, 11 are formed by bending a stainless steel plate (elastic metal plate). Each of the springs 11 and 11 has a base portion 21 and a pair of pressing pieces 22 formed by bending both side portions of the base portion 21 to one side in the thickness direction of the base portion 21 (right side in FIGS. 5 to 6). 22. The springs 11, 11 configured in this way are locked at a plurality of locations in the circumferential direction of the cage 12 by locking the base 21 to the support plate portions 19, 19. In this state where the springs 11 and 11 are locked to the cage 12, the tip portions of the pair of pressing pieces 22 and 22 constituting the springs 11 and 11 are respectively connected to the rollers 10 and 10. Elastically contacts the rolling surface. Then, with these pressing pieces 22, 22, the rollers 10, 10 are directed toward a narrow portion in the radial direction of the cylindrical space 23 existing between the cam surface 13 and the cylindrical surface 15. The direction is elastically pressed in the same direction. As a result, the roller clutch 5 can be switched between the locked state and the overrun state during the operation described below.

  When the roller clutch 5 configured as described above is used, the outer ring 8 is fitted into the pulley element 2 and the inner ring 9 is fitted to the sleeve 3. When the pulley element 2 and the sleeve 3 tend to rotate relative to each other in a predetermined direction, that is, the outer ring 8 fitted and fixed to the pulley element 2 is compared with the inner ring 9 fitted and fixed to the sleeve 3. When the springs 11 and 11 tend to rotate relative to the direction in which the rollers 10 and 10 are pressed (rightward in FIG. 5 = clockwise), the rollers 10 and 10 are in the cylindrical space. Of 23, it bites into a narrow portion in the diameter direction. Then, relative rotation between the sleeve 3 and the pulley element 2 becomes impossible (locked state), and rotation is transmitted between the sleeve 3 and the pulley element 2.

  On the other hand, the pulley element 2 and the sleeve 3 are opposite to the predetermined direction, that is, the pulley element 2 is against the sleeve 3 and the springs 11 and 11 are connected to the rollers 10 and 10. When there is a tendency to rotate in the opposite direction to the direction of pressing (left side in FIG. 5 = counterclockwise direction), the rollers 10 and 10 resist the elasticity of the springs 11 and 11. The cylindrical space 23 is retracted to a wide portion in the diameter direction so that the pulley element 2 and the sleeve 3 can rotate relative to each other (overrun state), and a rotational force is generated between the pulley element 2 and the sleeve 3. Will not be transmitted.

  In the case of constituting the roller clutch 5 as described above, the cylindrical surface 15 and the cam surface 13 in contact with the rollers 10 and 10 are formed directly on the inner peripheral surface of the driven pulley 3 and the outer peripheral surface of the sleeve 3, respectively. There is also. Further, the arrangement of the cylindrical surface 15 and the cam surface 13 in the radial direction may be reversed to the above-described structure. That is, the cylindrical surface 15 may be formed on the outer peripheral surface of the inner ring 9, and the cam surface 13 may be formed on the inner peripheral surface of the outer ring 8. In this case, when the outer ring 8 rotates in the direction opposite to the pressing direction of the springs 11, 11, the outer ring 8 enters a locked state. When the outer ring 8 rotates in the same direction as the pressing direction, the outer ring 8 enters an overrun state.

  When the pulley device 1 with built-in roller clutch of the present example configured as described above is used as a pulley device for an alternator, for example, a rotational force is transmitted from a pulley over which an endless belt is stretched to the rotating shaft of the alternator. However, the rotational force is not transmitted from the rotating shaft to the pulley. As a result, it is possible to prevent the endless belt and the pulley element from rubbing due to fluctuations in the rotational angular velocity of the crankshaft. Further, it is possible to prevent the endless belt from being shortened due to the generation of abnormal noise called squealing or wear, and to increase the power generation amount of the alternator. As described above, since the operation when the roller clutch built-in pulley device 1 is used in the alternator is widely known, detailed description thereof is omitted.

  As described above, the roller clutch 5 incorporated in the pulley device 1 with a built-in roller clutch makes the pressing pieces 22 and 22 of the springs 11 and 11 directly contact the rolling surfaces of the rollers 10 and 10, respectively. These rollers 10 and 10 are pressed. Further, when the roller clutch 5 is overrun, a force acts in a direction (counterclockwise in FIG. 5) to push back the pressing pieces 22 and 22 from the rollers 10 and 10 to the springs 11 and 11. Therefore, at the time of overrun, the pressing pieces 22 and 22 and the rolling surfaces of the rollers 10 and 10 come into strong contact with each other. At this time, due to the rotation of the rollers 10 and 10, the pressing pieces 22 and 22 are brought into sliding contact with the rolling surfaces of the rollers 10 and 10. Each of these rollers 10 and 10 is formed of a hard metal such as bearing steel, and each of the springs 11 and 11 is formed of a stainless steel plate or the like. Therefore, each of the pressing pieces 22 and 22 and each of the rollers 10 is formed. The sliding contact portions with the 10 rolling surfaces are in contact with the iron-based metals and are likely to wear. In this way, when the springs 11 and 11 and the rollers 10 and 10 are worn, the product life is shortened.

  In the structure in which the rollers 10 and 10 are pressed by the pressing pieces 22 and 22, it is difficult to control the posture of the rollers 10 and 10. When the cylindrical space 23 between the cylindrical surface 15 and the cylindrical surface 15 moves in the circumferential direction, it may be inclined. That is, the springs 11 and 11 press the rollers 10 and 10 by the pressing pieces 22 and 22 that are spaced apart in the axial direction of the roller clutch 5. For this reason, when the force of the same magnitude does not act on each of the rollers 10 and 10 from both of the pressing pieces 22 and 22, such as when the elastic forces of the pressing pieces 22 and 22 are different from each other, These rollers 10 and 10 are inclined. As described above, when the rollers 10 and 10 are inclined, the rollers 10 and 10 are less likely to bite into a portion of the cylindrical space 23 having a small diametrical width, or the pressing pieces 22 and 22. Is partially squeezed to cause the springs 11 and 11 to sag. As a result, a malfunction such as the inability to quickly switch between overrun and locked state is caused.

Japanese Patent Laid-Open No. 11-63170 Japanese Patent Publication No.7-72585 JP 2002-130433 A

  In view of the circumstances as described above, the present invention was invented to prevent the product life of a roller clutch from being shortened or causing a malfunction due to direct contact of each spring with each roller. .

The roller clutch of the present invention includes an outer ring equivalent member, an inner ring equivalent member, a cam surface, a cylindrical surface, a plurality of rollers, a cage, and a plurality of springs, as in the conventional structure described above.
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 an unevenness extending in the circumferential direction formed on one of the inner peripheral surface of the outer ring equivalent member and the outer peripheral surface of the inner ring equivalent member.
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 retainer is disposed in the cylindrical space and holds the rollers in a rollable manner.
In particular, in the roller clutch of the present invention, each of the springs is respectively locked to a member that forms the cam surface or a part of another member that rotates together with the member. The rollers are pressed in the same direction with respect to the circumferential direction.

  In the case of the roller clutch of the present invention configured as described above, each roller is pressed by each spring through a cage, so that each roller does not come into direct contact with each spring. For this reason, damage to each of these springs and each roller can be suppressed, and a decrease in durability can be suppressed. Moreover, since each said roller is pressed by the said holder | retainer, it is easy to stabilize the attitude | position of these each roller. For this reason, it is possible to prevent malfunction of the roller clutch.

In order to carry out the present invention, preferably, as described in claim 2, the cage is made of a synthetic resin.
If comprised in this way, the abrasion in the sliding contact part of the said holder | retainer and the rolling surface of each said roller can be suppressed.
Preferably, as described in claim 3, each roller is freely held only in a rolling manner in a pocket of a cage for holding each roller.
If comprised in this way, the attitude | position of each said roller can be stabilized reliably.
Preferably, as described in claim 4, the same number of the springs as the rollers are arranged, or as described in claim 5, the number of the springs is set to be equal to the number of the rollers. These springs are arranged at equal intervals in the circumferential direction.
When the same number of the springs as the rollers are arranged, the pressing force of the springs can be secured stably over the entire circumference.
On the other hand, when the number of the springs is smaller than the number of the rollers, the number of the rollers can be increased, so that the torque capacity of the roller clutch can be increased.
Furthermore, as described in claim 6, in the case of the pulley device with a built-in roller clutch incorporating the roller clutch described in any one of claims 1 to 5 as described above, a structure having excellent durability can be obtained. .

  1 and 2 show Embodiment 1 of the present invention. The feature of this example is that the springs 11a and 11a constituting the roller clutch 5a are not brought into direct contact with the rollers 10 and 10, and the rollers 10 and 10 are moved in a predetermined direction (clockwise in FIG. 1, FIG. 2). The right direction). Since the other structure and operation are as described above, the following description will focus on the features of this example. In the case of this example, each of the springs 11a and 11a is locked to a part of the inner ring 9a. That is, in this example, the cam surface 13 a is formed on the outer peripheral surface of the inner ring 9 a and the cylindrical surface 15 is formed on the inner peripheral surface of the outer ring 8. Locking protrusions 24 and 24 are formed at a plurality of locations in the circumferential direction of the cam surface 13a so as to protrude radially outward. The springs 11a and 11a are locked to the locking protrusions 24 and 24, respectively.

  Further, recesses 14a, 14a are formed in a portion between the locking projections 24, 24 in the circumferential direction. These locking projections 24, 24 and these recesses 14a, 14a are alternately formed at equal intervals in the circumferential direction on the outer peripheral surface of the inner ring 9a. In addition, you may form each said latching protrusion 24,24 in another member rotated with the said inner ring | wheel 9a. For example, as shown in FIG. 4 described above, another member having locking projections 24, 24 on the outer peripheral surface is provided on the outer peripheral surface of the inner ring 9 having a conventional structure so as not to impair the function of the recesses 14, 14. It can also be fitted and fixed. If comprised in this way, the inner ring | wheel 9 of a conventional structure can be used as it is.

  The springs 11a and 11a are formed by bending a stainless steel plate material such as SUS304, and are engaged with the locking projections 24 and 24 formed on the outer peripheral surface of the inner ring 9a. It can be stopped. In other words, each of the springs 11a and 11a includes a locking portion 25 that is locked to the locking protrusions 24 and 24 and a pressing portion 26 that elastically presses a part of the cage 12a. Among these, the latching | locking part 25 is formed in the U shape opened to radial direction inner side, and has latching plate part 27a, 27b. Then, the springs 11a, 11a are not rattled to the locking projections 24, 24 so that the locking portions 25 are covered from the radially outer sides of the locking projections 24, 24. Lock.

  That is, the interval between the inner side surfaces of the locking plate portions 27a and 27b in the free state is slightly smaller than the circumferential width of the locking projections 24 and 24. Therefore, in the state where the locking portion 25 is locked to the locking projections 24, 24, the locking plate portions 27a, 27b are respectively disposed on both circumferential sides of the locking projections 24, 24. Abuts elastically. For this reason, each said spring 11a, 11a is latched by these each latching protrusion parts 24 and 24 without rattling. In addition, the shape of each of these springs can be made as shown in FIGS. 5 to 6 by changing the locking method. Similarly, a compression coil spring can be used as the spring.

  As described above, the springs 11a and 11a press the retainer 12a in the same direction with respect to the circumferential direction while being locked to the locking protrusions 24 and 24. The cage 12a is made of synthetic resin. As this synthetic resin, a cage material used for a general rolling bearing, for example, a material in which glass fiber is mixed in a thermoplastic resin such as polytetrafluoroethylene resin (PTFE), polyamide 46, polyamide 66, etc. is preferably used. it can. In addition to the synthetic resin, a non-ferrous metal material having a self-lubricating property such as a copper alloy may be used as the material of the cage 12a.

  The retainer 12a includes a pair of rim portions 16a and 16a each having an annular shape, and connecting portions 17a and 17a for connecting inner surfaces of the rim portions 16a and 16a, as in the conventional structure. Is provided. The portions surrounded by the rim portions 16a, 16a and the two sets of connecting portions 17a, 17a adjacent to each other in the circumferential direction are pockets 20a, 20b, respectively. 10 and 10 and the springs 11a and 11a are provided. Unlike the conventional structure, the cage 12a is not provided with a protruding piece that can be engaged with the recesses 14a, 14a on the inner peripheral surfaces of the rim parts 16a, 16a. Therefore, the cage 12a can be displaced in the circumferential direction with respect to the inner ring 9a.

  In this example, the same number of the springs 11a and 11a as the rollers 10 and 10 are arranged. Thereby, the pressing force by each of these springs 11a and 11a can be ensured stably over the entire circumference. For this reason, the number of pockets 20a and 20a for holding the rollers 10 and 10 and the number of pockets 20b and 20b for installing the springs 11a and 11a are the same. In the case of the illustrated example, the widths of the pockets 20a, 20a and the pockets 20b, 20b in the circumferential direction are different from each other, but the circumferential widths of the locking projections 24, 24 are set to an appropriate size. For example, the widths of the pockets 20a and 20b in the circumferential direction may be the same. If comprised in this way, the punching process etc. at the time of forming each of these pockets 20a and 20b will become easy, and besides the manufacturing cost of the said holder | retainer 12a can be reduced, it becomes unnecessary to distinguish each of these pockets 20a and 20b. As a result, assembly work is facilitated.

  Further, in this example, the width of each of the pockets 20a, 20a in the circumferential direction is the same as or slightly larger than the outer diameter of the rollers 10, 10, so that the rollers 10, 10 is held freely in the pockets 20a and 20a only by rolling. For this reason, the posture of each of the rollers 10 and 10 can be reliably stabilized. If the rollers 10 and 10 are displaceable in the circumferential direction of the cage 12a, there is a possibility that the cage 12a will collide strongly when the rollers 10 and 10 are pressed. As a result, the contact portion between the retainer 12a and each of the rollers 10 and 10 is damaged, and abnormal noise is likely to occur when the rotational speed of the roller clutch 5a varies. On the other hand, if the rollers 10 and 10 are held in the pockets 20a and 20a only in a rollable manner, the rollers 10 and 10 and the retainer 12a may be damaged, or the roller clutch 5a It is possible to prevent abnormal noise from occurring during operation.

  Although different from the illustrated example, the shape of the inner surface of the connecting portions 17a and 17a located on both sides in the circumferential direction of the pockets 20a and 20a holding the rollers 10 and 10 is changed to the respective rollers 10 and 20a. If the arcuate concave surface having a radius of curvature slightly larger than the outer diameter of 10 is used, the rollers 10 and 10 are more reliably displaced in the radial direction, for example, during overrun. It can be held so that nothing happens.

  In the case of this example, the retainer 12a is provided with pockets 20b and 20b for installing the springs 11a and 11a in addition to the pockets 20a and 20a for holding the rollers 10 and 10. These pockets 20b and 20b are arranged at positions facing the respective locking projections 24 and 24. Therefore, in the state where the cage 12a is arranged around the inner ring 9a, the locking projections 24, 24 exist in the pockets 20b, 20b. For this reason, in the case of the present example, the retainer 12a is disposed on the outer peripheral surface of the inner ring 9a while combining and combining the members divided into two. That is, in the case of this example, since the locking protrusions 24, 24 exist in the pockets 20b, 20b, the cage 12a cannot be disposed on the outer peripheral surface of the inner ring 9a unless it is divided into a plurality of pockets. For this reason, in the case of this example, the member divided into two in the radial direction or the axial direction is combined and combined while being arranged on the outer peripheral surface of the inner ring 9a to form the cage 12a.

  The cage 12a configured as described above is formed by the pressing portion 26 that constitutes each of the springs 11a and 11a and is latched to each of the latching protrusions 24 and 24 existing in the pockets 20b and 20b. , Pressed in a predetermined direction. That is, the pressing portion 26 is formed by bending outward in the radial direction from the distal end portion of the locking plate portion 27b existing in the pressing direction of the retainer 12a among the locking plate portions 27a and 27b. Then, the retainer 12a is elastically brought into contact with the one end in the circumferential direction (the left side in FIGS. 1 and 2) of the connecting portions 17a and 17a of the retainer 12a. Is pressed in a predetermined direction (clockwise in FIG. 1, right in FIG. 2). In the case of this example, since the cage 12a is provided so as to be slightly displaceable in the circumferential direction with respect to the inner ring 9a as described above, the retainer 12a is provided by the pressing portions 26 constituting the springs 11a and 11a. When pressed, it is displaced in the pressed direction.

  In addition, the other circumferential side surface (the right side surface in FIGS. 1 and 2) of the connecting portions 17a and 17a of the retainer 12a moved in a predetermined direction as described above is in contact with the rollers 10 and 10, respectively. The rollers 10 and 10 are pressed in the predetermined direction. As a result, each of these rollers 10 and 10 moves toward a portion where the width in the diameter direction of the cylindrical space 23 existing between the cam surface 13a and the cylindrical surface 15 is narrow.

  In the case of this example configured as described above, the rollers 10 and 10 are pressed by the springs 11a and 11a through the cage 12a. There is no contact with the springs 11a, 11a. For this reason, damage to each of these springs 11a and 11a and each of the rollers 10 and 10 can be suppressed. In particular, in the case of this example, since the cage 12a that presses the rollers 10 and 10 is made of synthetic resin, wear hardly occurs due to sliding contact with the rolling surfaces of the rollers 10 and 10. That is, the synthetic resin has a self-lubricating property in contact with a metal, and does not cause an adhesion phenomenon like the contact between metals. For this reason, wear hardly occurs due to contact with metal, and wear at the sliding contact portion with the rolling surface of each of the rollers 10 and 10 can be suppressed. As a result, it is possible to suppress a decrease in product life of the roller clutch 5a. In addition, when a non-ferrous metal is used as the material of the cage 12a, it has more wear resistance than the contact of the same kind of metals, so that the wear at the sliding contact portions with the rolling surfaces of the rollers 10 and 10 is again. Can be suppressed.

  Further, since the rollers 10 and 10 are pressed by the cage 12a, the postures of the rollers 10 and 10 are easily stabilized. For this reason, it is possible to prevent the roller clutch 5 from malfunctioning, such as being unable to quickly switch between overrun and locked state. Further, when the roller clutch 5a of this example configured as described above is incorporated in a pulley device with a built-in roller clutch as shown in FIG. 4, the pulley device with a built-in roller clutch has durability. An excellent structure can be obtained.

  FIG. 3 shows a second embodiment of the present invention. In the case of this example, the number of springs 11a, 11a is smaller than the number of rollers 10, 10. Specifically, the springs 11a and 11a are arranged at three equal intervals in the circumferential direction. For this reason, the number of the locking projections 24, 24 provided on the cam surface 13b of the inner ring 9b is also three. The number of the springs 11a, 11a may be more or less than three. For example, it can be one. However, when the number of springs is reduced in this way, the necessary pressing force cannot be secured unless a spring having a large elasticity is used. There is also a problem that it is difficult to ensure a stable pressing force in the circumferential direction. For this reason, it is preferable that the number of springs be three or more and be arranged at equal intervals in the circumferential direction. In the case of this example configured as described above, since the number of the rollers 10 and 10 can be increased, the torque capacity of the roller clutch can be increased. Other configurations and operations are the same as those of the first embodiment.

  In the first and second embodiments, the cam surface is formed on the outer peripheral surface of the inner ring. However, the present invention is also applicable to a structure in which the cam surface is formed on the inner peripheral surface of the outer ring. It is. That is, the cam surface is formed on the inner peripheral surface of the outer ring, and a locking projection for locking each spring is also formed. On the other hand, a cylindrical surface is formed on the outer peripheral surface of the inner ring. And each roller is pressed via a holder | retainer by each said spring latched by these each latching protrusion.

The figure similar to FIG. 5 which shows Example 1 of this invention in a locked state. The figure which took out the holder | retainer, the spring, and the roller, and was seen from the radial direction outer side of FIG. Sectional drawing which shows Example 2 of this invention assembled | attached to the outer peripheral surface of the inner ring | wheel with the holder | retainer, the spring, and the roller. Sectional drawing which shows an example of the pulley apparatus with a built-in roller clutch conventionally known. FIG. 5 is a cross-sectional view taken along the line AA in FIG. The partial perspective view shown in the state which took out only a holder | retainer and a spring.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Pulley device with built-in roller clutch 2 Pulley element 3 Sleeve 4 Ball bearing 5, 5a, 5b Roller clutch 6 Large diameter part 7 Small diameter part 8 Outer ring 9, 9a, 9b Inner ring 10 Roller 11, 11a Spring 12, 12a Cage 13, 13a, 13b Cam surface 14, 14a Recess 15 Cylindrical surface 16, 16a Rim part 17, 17a Connection part 18 Projection piece 19 Support plate part 20, 20a, 20b Pocket 21 Base part 22 Press piece 23 Cylindrical space 24 Locking projection part 25 Locking part 26 Pressing part 27a, 27b Locking plate part

Claims (6)

  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 The cam surface, which is an uneven surface extending in the circumferential direction, is formed on the other peripheral surface, and a plurality of the cam surfaces are provided in a cylindrical space between the cam surface and the cylindrical surface. A roller clutch that is disposed in the cylindrical space and that holds the rollers in a rollable manner, and a plurality of springs. The springs form the cam surface. A roller clutch, wherein the roller clutches are respectively engaged with the member or another member rotating together with the member and press the rollers in the same direction with respect to the circumferential direction via the cage.   The roller clutch according to claim 1, wherein the cage is made of synthetic resin.   The roller clutch according to any one of claims 1 to 2, wherein each roller is held only in a rolling manner within a pocket of a cage for holding each roller.   The roller clutch according to claim 1, wherein each spring is arranged in the same number as each roller.   The roller clutch according to any one of claims 1 to 3, wherein the number of each spring is smaller than the number of each roller, and the respective springs are arranged at equal intervals in the circumferential direction.   An inner diameter side member fixed to the end portion of the rotating shaft, and a cylindrical outer diameter side provided with a belt groove around the inner diameter side member, concentrically arranged with the inner diameter side member, and for belting around the outer peripheral surface. 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. Roller clutch built-in type pulley apparatus, characterized in that a roller clutch according to either one.

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