JP4706390B2 - Roller clutch - Google Patents

Description

  The present invention relates to an improvement in a roller clutch that is used by being incorporated in, for example, a reel for fishing gear, a business machine such as a printer or a copying machine.

  For example, as described in Patent Documents 1 and 2, a roller clutch has been conventionally incorporated into a reel for fishing gear. That is, a structure has been conventionally known in which a roller clutch is provided between a handle shaft that fixes a handle for winding a fishing line at an end thereof and a part of a cover of a reel and only allows rotation in a predetermined direction. ,It has been implemented. Specifically, when the handle is rotated to wind up the fishing line, the roller clutch is idled (overrun), so that the fishing line can be wound up. On the other hand, when the fishing line tends to be fed out by pulling the fish or the like, the roller clutch is locked to prevent the fishing line from being fed out.

Further, as described in Patent Document 3, for example, a structure in which a one-way clutch such as a roller clutch is incorporated in a printer is also known. In the case of the structure described in Patent Document 3, the above-described one-way clutch is incorporated in a roller for fixing toner to paper, and this roller is driven even when the rotational force is hardly transmitted to this roller. The paper can be discharged. And office machines such as such printers, concerning the basic structure of the roller clutches used incorporated into a reel for such as the aforementioned fishing tackle, will be described with reference to FIG.

  The roller clutch 1 includes an inner ring 2 corresponding to an inner ring equivalent member, an outer ring 3 corresponding to an outer ring equivalent member, a plurality of rollers 4, a cage 5, a plurality of springs 6, 6 and. Of these, the inner ring 2 and the outer ring 3 are each formed in a cylindrical shape by a hard metal plate material of carburized steel such as bearing steel or SCM415. For example, the inner ring 2 is fitted and fixed to the outer peripheral surface of the handle shaft of the reel, and the outer ring 3 is fixed to the inner peripheral surface of a part of the cover of the reel. A cylindrical intermediate surface 7 is an axially intermediate portion that contacts at least the rollers 4 among the outer peripheral surface of the inner ring 2. At the same time, the inner peripheral surface of the outer ring 3 is a cam surface 8. That is, a plurality of recesses 9 each called a ramp portion are formed on the inner peripheral surface of the outer ring 3 at equal intervals in the circumferential direction, and the inner peripheral surface of the outer ring 3 is used as the cam surface 8.

  In the cylindrical space between the cam surface 8 and the cylindrical surface 7, the cage 5 and the plurality of rollers 4 and springs 6 and 6 are provided. Of these, the cage 5 is formed integrally with a bowl-shaped cylindrical shape using a synthetic resin (for example, a synthetic resin such as polyamide 46 mixed with about 20% glass fiber), and each pair is an annular shape. Rim portion 10 and pillar portions 11 and 11 for connecting the inner side surfaces of both rim portions 10 to each other. Such a retainer 5 rotates with respect to the outer ring 3 by engaging the engaging projections 12 formed on the outer peripheral surfaces of the rim portions 10 with the recesses 9 constituting the cam surface 8. It is impossible.

On the other hand, between the cage 5 and the rollers 4, the rollers 4 are directed toward the shallow side of the recesses 9 and pressed in the same direction (left direction in FIG. 5 ) with respect to the circumferential direction . The springs 6 are provided. Each of these springs 6 and 6 is formed by bending a stainless steel plate material (elastic metal plate) such as SUS304. And in the state which each such springs 6 and 6 were latched to each pillar part 11 and 11 of the said holder | retainer 5, respectively, the press piece 13 which comprises these each spring 6 and 6 is each said roller 4 respectively. It is made to contact elastically with the rolling surface. As a result, the rollers 4 can be elastically pressed in the same direction in the circumferential direction toward a narrow portion in the radial direction of the cylindrical space between the cylindrical surface 7 and the cam surface 8. As a result, as described below, during operation, the roller clutch 1 can be switched between a locked state and an overrun state.

  The operation of the roller clutch 1 configured as described above is as follows. First, when the inner ring 2 rotates relative to the outer ring 3 in the same direction as the pressing direction of the rollers 4 by the springs 6, 6, the rollers 4 from the cylindrical surface 7 and the cam surface 8. In addition, a force in the same direction as the pressing direction is applied. As a result, each of the rollers 4 is displaced toward a narrow portion in the radial direction of the cylindrical space, and bites into the portion in a wedge shape. As a result, the outer ring 3 and the inner ring 2 are locked, and the inner ring 2 cannot rotate with respect to the outer ring 3.

  On the other hand, when the inner ring 2 rotates in the direction opposite to the pressing direction with respect to the outer ring 3, a force in the direction opposite to the pressing direction acts on each roller 4 from the cylindrical surface 7. As a result, each of the rollers 4 tends to be displaced toward a wide portion in the radial direction of the cylindrical space. At this time, the rollers 4 bend the pressing pieces 13 constituting the springs 6 and 6. As described above, each roller 4 displaced toward the wide portion can be freely rolled and slightly displaced in the portion. As a result, an overrun state occurs between the outer ring 3 and the inner ring 2, and the inner ring 2 can rotate with respect to the outer ring 3.

As described above, the cage 5 of the roller clutch 1 cannot be rotated with respect to the outer ring 3 (some relative rotation is possible due to a gap existing in the engaging portion between the concave portion 9 and the engaging convex portion 12). On the other hand, rotation with respect to the inner ring 2 is possible. For this purpose, a gap is provided between the inner peripheral surface of the cage 5 and the cylindrical surface 7 of the inner ring 2. Further, when incorporating the roller clutch 1, for example, a reel for fishing, in general, as shown in FIG. 6, externally fitted to the inner ring 2 to the handle shaft 14 of the reel. However, when there is rattling (gap) in the fitting portion between the inner ring 2 and the handle shaft 14, a time lag occurs when the roller clutch 1 shifts from the overrun state to the locked state for the following reason. May occur.

  That is, at the time of overrun, each roller 4 enters the inner part of each recess 9 and the diameter of the inscribed circle of each roller 4 increases. Accordingly, if there is rattling in the fitting portion between the inner ring 2 and the handle shaft 14, the inner ring 2 can move in the radial direction with respect to the handle shaft 14 during overrun. On the other hand, the outer ring 3 is fitted and fixed to a part of the inner peripheral surface of the cover constituting the reel, and the handle shaft 14 is disposed concentrically with the inner peripheral surface of the cover. Therefore, the outer ring 3 and the handle shaft 14 are arranged concentrically, and the retainer 5 supported by the outer ring 3 and the handle shaft 14 are substantially concentric. Therefore, when there is rattling in the fitting portion between the inner ring 2 and the handle shaft 14, the inner ring 2 can move in the radial direction with respect to the handle shaft 14 and the cage 5 during overrun. .

  When the roller clutch 1 shifts from the overrun state to the locked state, the cylindrical space in which each roller 4 exists between the inner peripheral surface of the outer ring 3 and the outer peripheral surface of the inner ring 2 as described above. Displacement toward a narrow portion in the radial direction of And the said outer ring | wheel 3 and the said inner ring | wheel 2 will be in a locked state (relative rotation impossible) by biting into the said part in a wedge shape. In order to achieve the locked state, it is necessary that all the rollers 4 existing at a plurality of locations in the circumferential direction of the cylindrical space bite into a portion where the radial width of the cylindrical space is narrow. For this purpose, the center axis of the inscribed circle of each roller 4 and the center axis of the inner ring 2 need to coincide with each other. As described above, the inner ring 2 can move in the radial direction with respect to the handle shaft 14 and the retainer 5 during overrun due to rattling with the handle shaft 14. For this reason, radial runout occurs in the inner ring 2 in an overrun state. As a result, the center axis of the inscribed circle of each roller 4 held by the cage 5 and the center axis of the inner ring 2 are unlikely to coincide with each other during overrun. The transition from the overrun state to the locked state is performed after the center axis of the inscribed circle of each roller 4 and the center axis of the inner ring 2 coincide with each other. The time required for the transition from the overrun state to the locked state becomes longer by the time required to match the axes (time lag occurs).

  As described above, if there is a time lag before shifting from the overrun state to the locked state, for example, when the roller clutch 1 is incorporated in a reel for fishing gear, it may be uncomfortable for a person operating this reel. . In order to solve such a problem, it is conceivable to reduce the gap between the inner peripheral surface of the cage 5 that holds the rollers 4 and the cylindrical surface 7 that constitutes the outer peripheral surface of the inner ring 2. That is, the inner diameter of the cage 5 is reduced, and the inner circumferential surface of the cage 5 and the cylindrical surface 7 are brought close to each other over the entire circumference. The distance that the inner ring 2 can move in the radial direction in the overrun state (the radial play) is set to the maximum clearance of the fitting portion between the inner ring 2 and the handle shaft 14, in other words, to the handle shaft 14. On the other hand, when only this inner ring 2 is combined, the inner ring 2 is set to be smaller than the distance that can be moved in the radial direction with respect to the handle shaft 14. With this configuration, regardless of the backlash between the inner ring 2 and the handle shaft 14, the inner ring 2 can be prevented from shaking in the radial direction during overrun, and the inner diameter of each roller 4 held by the cage 5 can be reduced. The deviation between the center axis of the tangent circle and the center axis of the inner ring 2 can be reduced. As a result, the time lag can be reduced.

  However, when the inner peripheral surface of the cage 5 and the cylindrical surface 7 are brought close to each other over the entire periphery in this way, the lubricating oil is difficult to spread between these surfaces. For this reason, there is a possibility that the friction torque when the inner ring 2 rotates relative to the cage 5 increases. As a result, the overrun torque increases when the inner ring 2 rotates relative to the cage 5 and the outer ring 3 during overrun, which is not preferable.

  On the other hand, when the roller clutch 1 is in an overrun state, the cage 5 tends to rotate in a predetermined direction due to the elastic force of the springs 6 and 6 existing between the rollers 4 and the column portions 11 and 11. Become. That is, when shifting to the overrun state, each of the rollers 4 moves toward a portion of the cylindrical space of the roller clutch 1 having a large radial width (right side in the illustrated example). The movement causes the springs 6 and 6 to bend, and based on the elastic restoring force of the springs 6 and 6, a force in the same direction as the moving direction of the rollers 4 acts on the pillars 11 and 11. As a result, the cage 5 tends to rotate in the same direction as the moving direction of the rollers 4. However, the retainer 5 is engaged with the recesses 9 formed on the inner peripheral surface of the outer ring 3 by the engagement convex portions 12 formed on the outer peripheral surfaces of the rim portions 10 of the retainer 5, so that the retainer 5 is On the other hand, there is no relative rotation over the circumferential clearance between each of the engaging convex portions 12 and the concave portions 9.

As described above, the cage 5 tends to rotate with respect to the outer ring 3 during overrun. However, if the clearance between the outer circumferential surface of the cage 5 and the inner circumferential surface of the outer ring 3 is large, the overrun state will occur. Therefore, there is a possibility that the followability of each roller 4 at the time of the locked state becomes worse, and further, it becomes impossible to lock. That is, as shown in FIG. 7 , if the clearance between the outer peripheral surface of the retainer 5 (including the outer peripheral surface of the engaging projection 12) and the inner peripheral surface of the outer ring 3 is large, the roller clutch 1 is in an overrun state. In this case, the leading end of the engaging projection 12 in the rotational direction (rightward in the illustrated example) may bite into the portion of the inner peripheral surface of the outer ring 3 that is out of the recess 9.

  As described above, when a part of the engaging convex portion 12 bites into a portion of the inner peripheral surface of the outer ring 3 that is disengaged from the concave portion 9, each roller 4 has a radial width in the cylindrical space so as to be locked. When moving toward a narrow portion (left side in the illustrated example), the movement of the cage 5 is delayed or before each roller 4 bites into the portion, the column portion 11 constituting the cage 5 There is a possibility of coming into contact with the side surface. In the former case, there is a delay (time lag) before each of the rollers 4 bites into the portion. Further, in the latter case, the rollers 4 cannot contact the column portion 11 of the cage 5 and can bite into the narrow portion of the cylindrical space in the radial direction. There is also. In order to prevent the time lag or the inability to lock, the number of rollers 4 that can be incorporated into the roller clutch 1 is reduced when the interval between the column portions 11 adjacent to each other in the circumferential direction is increased. Since the load capacity of 1 will fall, it is not preferable.

JP 2000-116923 A JP 2001-17042 A JP 2000-242126 A

  The roller clutch of the present invention has been invented to realize a structure capable of reducing the time lag when shifting from the overrun state to the locked state, or preventing the lock from becoming impossible. .

As in the conventional structure shown in FIG. 5 , 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 rollers. And a spring.
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 uneven in the circumferential direction, and 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.
The cylindrical surface is formed on the other peripheral surface of the inner peripheral surface of the outer ring equivalent member and the outer peripheral surface of the inner ring equivalent member.
Each of the rollers is provided in a cylindrical space between the cam surface and the cylindrical surface.
The cage is formed in a substantially cylindrical shape, and is disposed in the cylindrical space in a state in which relative rotation with respect to the member forming the cam surface is prevented, and the rollers are rolled and circumferentially arranged. It is held so as to be slightly displaceable with respect to the 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 of the present invention, convex portions projecting toward the cylindrical surface are provided at a plurality of locations in the circumferential direction of the circumferential surface opposite to the cylindrical surface, of the inner and outer circumferential surfaces of the cage. Forming. And the distance that can be moved in the radial direction of the member that formed this cylindrical surface is present in the fitting portion between the member that formed this cylindrical surface and the other member that fits this member, The gap between the two members is smaller than the gap associated with the radial relative displacement.

The roller clutch of the present invention configured as described above is a member that forms this cylindrical surface during overrun regardless of the backlash of the fitting portion between the member that forms the cylindrical surface and the member that fits this member. Thus, the deviation between the center axis of the inscribed circle or the circumscribed circle of each roller held by the cage and the center axis of the member forming the cylindrical surface can be reduced. As a result, the time lag when the overrun state changes to the locked state can be reduced. In addition, since a convex portion is formed on the peripheral surface of the cage in order to reduce the deviation between the central axes, it is easy to distribute the lubricating oil between the peripheral surface of the cage and the cylindrical surface. The increase in overrun torque can be suppressed.

In order to implement the roller clutch of the present invention, preferably, an oil groove is formed on the surface of each convex portion as in the invention described in claim 2. As the oil groove, for example, a knurled groove or dimple can be employed. Furthermore, it is good also as a groove | channel inclined in the predetermined direction according to the overrun direction.
If comprised in this way, it will become easy to take in lubricating oil between each convex part and a cylindrical surface, and the increase in overrun torque can be suppressed more.
Alternatively, as in the invention described in claim 3, each of the grooves constituting the oil groove can be inclined in the radially inward direction toward the overrun direction of the inner ring.
If configured in this manner, the cylindrical surface of the inner ring and each groove constituting the oil groove can be brought into smooth contact during overrun, and these grooves can be hardly damaged.

1 to 3 show Embodiment 1 of the present invention corresponding to claims 1 and 2. The feature of the present embodiment is that the overrun torque is suppressed, and in order to reduce the time lag when shifting from the overrun state to the locked state, the inner surface of the retainer 5a facing the cylindrical surface 7 (see FIG. 5 ) . It is in the point which forms the convex parts 15 and 15 in the peripheral surface several places. Since the structure and operation of other parts are the same as those of the conventional structure shown in FIG. 5 described above, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on the characteristic parts of this embodiment.

In the case of the present embodiment, the convex portions 15 and 15 projecting radially inward are formed at a plurality of locations in the circumferential direction on the inner circumferential surface of the cage 5a. Each of these convex portions 15 and 15 is formed in a circular arc shape in cross section, and the protruding amount of each is the same. In addition, the diameter of the inscribed circle of each of the convex portions 15 and 15 is larger than the diameter of the cylindrical surface 7 that faces the inner peripheral surface of the cage 5a and constitutes the outer peripheral surface of the inner ring 2 (see FIG. 5 ) . Slightly larger. Further, the difference in diameter between the inscribed circle of each of the convex portions 15 and 15 and the cylindrical surface 7 is, for example, when the roller clutch of this embodiment is incorporated in a fishing reel, the inner ring 2 and the inner ring 2 It exists in the fitting part with the handle | steering-wheel shaft 14 (refer FIG. 6 ) which is a member to fit, and it is made smaller than the clearance gap linked to radial direction relative displacement of these inner ring | wheels 2 and the handle | steering-wheel axis | shaft 14. For this reason, the distance that the inner ring 2 can move in the radial direction in the overrun state is regulated by the difference in diameter between the inscribed circle of the convex portions 15 and 15 and the cylindrical surface 7.

  In the illustrated example, the convex portions 15 and 15 are formed on the inner peripheral surfaces of the rim portions 10 and 10 or the inner peripheral surfaces of the column portions 11 and 11 constituting the cage 5a, respectively. For this reason, the number of the convex portions 15 and 15 is the same as the number of the column portions 11 and 11. Note that the number of the convex portions 15 and 15 is determined by design in consideration of the sliding contact area with the cylindrical surface 7 and the like. For example, if it is desired to reduce the sliding contact area with the cylindrical surface 7, the number of the convex portions 15, 15 is reduced. However, in order to obtain the effect of the present invention, it is necessary to form these convex portions 15 and 15 at equal intervals in at least three circumferential directions, but the number of these convex portions 15 and 15 is too small. In the overrun, the radial runout of the inner ring 2 may not be sufficiently reduced. Accordingly, the number of the convex portions 15 is determined in consideration of this point.

  Moreover, the cross-sectional shape of each said convex part 15 and 15 is not restricted to circular arc shape, It can also be set as other shapes, such as trapezoid shape. Further, as shown in the figure, it can be elongated like a bank, or it can be a partially spherical projection. Among these, from the viewpoint of reducing the sliding contact area with the cylindrical surface 7, it is preferable to have an arc shape or a spherical protrusion shape as in the illustrated example. Furthermore, in the example shown in the drawing, the convex portions 15 and 15 are formed on the entire inner circumferential surface of the rim portions 10 and 10 to the entire inner circumferential surface of the column portions 11 and 11 of the cage 5a. However, for example, the pillar portions 11 and 11 may be divided into inner peripheral surfaces, or may be formed only on the inner peripheral surfaces of the rim portions 10 and 10 constituting the cage 5a. .

  In the case of the present embodiment, oil grooves 16 are formed on the surfaces of the convex portions 15 and 15, respectively. The oil groove 16 has a knurled shape in the illustrated example (described only in the central convex portion 15 in FIG. 1), but may be a groove having other shapes such as dimples. For example, as shown in FIG. 4, each groove constituting the oil groove 16 a formed on the surface of the convex portion 15 a may be inclined according to the overrun direction of the inner ring 2. That is, when the inner ring 2 overruns in the clockwise direction (arrow direction) in FIG. 4, each groove is inclined in the direction toward the radially inward as it goes in the overrun direction. If configured in this manner, the cylindrical surface 7 of the inner ring 2 and the grooves constituting the oil groove 16a can be brought into smooth contact during overrun, and these grooves are less likely to be damaged. In the case of the illustrated example, the respective grooves are exaggerated for the purpose of explanation.

When the cage 5a configured as described above is incorporated in the roller clutch 1 shown in FIG. 5 , for example, the cage 5a and the inner ring 2 are arranged concentrically, The tip portions of the convex portions 15 formed on the inner peripheral surface are in close proximity to the cylindrical surface 7 of the inner ring 2. The distance that the inner ring 2 can move in the radial direction in the overrun state is regulated by the difference in diameter between the inscribed circle of each of the convex portions 15 and 15 and the cylindrical surface 7 of the inner ring 2. And the clearance between the inner ring 2 and the handle shaft 14, which are present in the fitting portion between the inner ring 2 and the handle shaft 14. For this reason, regardless of the backlash of the fitting part between the inner ring 2 and the handle shaft 14, the over-running suppresses the radial vibration of the inner ring 2 and prevents the rollers 4 held by the cage 5 a from moving. The deviation between the center axis of the inscribed circle and the center axis of the inner ring 2 can be reduced. As a result, when shifting from the overrun state to the locked state, the time required to make the center axis of the inscribed circle of each roller 4 coincide with the center axis of the inner ring 2 can be shortened (time lag can be reduced).

  In the case of the present embodiment, convex portions 15 are formed on the inner peripheral surface of the cage 5a in order to reduce the deviation between the central axes. Therefore, the lubricating oil supplied (or enclosed) in the roller clutch 1 can be easily distributed between the inner peripheral surface of the cage 5a and the cylindrical surface 7. As a result, an increase in overrun torque can be suppressed as compared with the case where the gap between the entire inner peripheral surface of the cage 5a and the cylindrical surface 7 is reduced. Further, in the case of the present embodiment, since the oil grooves 16 are formed in the respective convex portions 15, 15, the lubricating oil is taken in between the tip portions of the respective convex portions 15, 15 and the cylindrical surface 7. It is possible to easily increase the overrun torque.

  In the present embodiment, the structure in which the cage 5a is supported on the outer ring 3 so as not to rotate relative to the outer ring 3 has been described. However, the present invention supports the structure in which the cage is supported on the inner ring so as not to rotate relative to the inner ring. It is also applicable to a structure in which engaging convex portions are formed at a plurality of locations on the inner peripheral surface of the rim portion and these engaging convex portions are engaged with a concave portion constituting a cam surface formed on the outer peripheral surface of the inner ring. . That is, in the case where the outer ring is structured to be movable in the radial direction during overrun due to the rattling of the fitting part with the member for fitting and fixing the outer ring, convex portions are formed at a plurality of locations on the outer peripheral surface of the cage. Then, these convex portions and the cylindrical surface constituting the inner peripheral surface of the outer ring are placed close to each other. Then, the distance that the outer ring can move in the radial direction in the overrun state is made smaller than the maximum clearance of the fitting portion between the outer ring and a member that fits the outer ring. Even in the case of such a structure, the circumscribed circle of each roller held by the cage is suppressed in the overrun while suppressing the radial runout of the outer ring, regardless of the rattling of the fitting portion. The deviation between the central axis of the outer ring and the central axis of the outer ring can be reduced. As a result, the time lag when shifting from the overrun state to the locked state can be reduced. Further, as in the first embodiment, an increase in overrun torque can be suppressed.

  The roller clutch according to the present invention is used for driving an auxiliary machine for an idling stop car, an alternator and a compressor for an automobile auxiliary machine, a starter motor constituting an automobile starting device, in addition to a reel for fishing gear and an office machine such as a printer. It can also be used by being incorporated in a roller clutch built-in pulley device that is used by being fixed to the end of a rotating shaft such as a motor.

The partial perspective view which shows the holder | retainer integrated in the structure of Example 1 of this invention in the state seen from radial inside. The figure which expands and shows a part of rim | limb part of a holder | retainer. The figure which expands and shows the convex part formed in the rim | limb inner peripheral surface of a holder | retainer. The fragmentary sectional view which exaggerates and shows another example of the oil groove formed in a convex part. The fragmentary sectional view which shows one example of the conventional structure. (A) is a perspective view showing a state before the inner ring is externally fitted to the handle shaft of the reel, and (B) is a perspective view showing a state after the external fitting. The enlarged view corresponding to the A section of Drawing 5 showing the unfavorable engagement state of the engagement convex part of a maintenance machine, and the crevice of an outer ring.

DESCRIPTION OF SYMBOLS 1 Roller clutch 2 Inner ring 3 Outer ring 4 Roller 5, 5a, 5b Cage 6 Spring 7 Cylindrical surface 8, 8a Cam surface 9, 9a Recessed part 10 Rim part 11 Column part
12 engaging convex part 13 pressing piece 14 handle shaft 15, 15a convex part 16, 16a oil groove

Claims (3)

  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 A substantially cylindrical shape which is disposed in the cylindrical space in a state in which relative rotation with respect to the roller and the member forming the cam surface is prevented, and holds each roller so as to be able to roll and slightly displace in the circumferential direction. A plurality of cages, each of which is provided between the cage and each of the rollers, and presses each of the rollers toward a narrow radial portion of the cylindrical space in the same direction with respect to the circumferential direction. A roller clutch with a spring The cylindrical surface is formed by forming convex portions projecting toward the cylindrical surface at a plurality of locations in the circumferential direction of the peripheral surface facing the cylindrical surface, of the inner and outer peripheral surfaces of the cage. The distance that the member can move in the radial direction in the overrun state exists in the fitting portion between the member that forms this cylindrical surface and the other member that fits this member. A roller clutch characterized in that it is smaller than the gap that leads to displacement.   The roller clutch according to claim 1, wherein an oil groove is formed on a surface of each convex portion. The cam surface is formed on the inner peripheral surface of the outer ring equivalent member, and the cage is disposed in the cylindrical space in a state of preventing relative rotation with respect to the outer ring equivalent member, and is formed on the surface of each convex portion. 3. The oil groove is present on the inner peripheral surface of the cage, and each of the grooves constituting the oil groove is inclined in a radially inward direction toward the overrun direction of the inner ring. Roller clutch.

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