JP2571919Y2 - Roller clutch with lock release mechanism - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION A roller clutch with an unlocking mechanism according to the present invention is a so-called index backstop for preventing reverse rotation in a conveying device such as a roller conveyor, for example. Used in a selection mechanism for selecting power transmission with time, a paper feed mechanism of a facsimile or a copying machine, or incorporated in a fishing reel.

[0002]

2. Description of the Related Art A roller clutch with an unlocking mechanism is incorporated in a reel which is one type of fishing gear, for example, for feeding or winding a fishing line. In the case of fishing using such a reel, for example, when the fishing line is entangled and the entanglement is corrected, the lock mechanism of the roller clutch is released so that the reel can freely rotate. On the other hand, when winding a fishing line on a reel, such as when catching a fish, the lock mechanism of the roller clutch is operated. As a result, only when the angler operates the operation handle, the reel rotates in the winding direction and winds the fishing line on the reel. Even if the angler releases his / her hand from the operation handle, the reel does not rotate due to the operation of the lock mechanism, so that the fishing line is not sent out.

[0003] As a roller clutch with an unlocking mechanism which is considered to be usable in the above-mentioned state, there is conventionally known, for example, one disclosed in Japanese Utility Model Laid-Open No. 55-154827. This conventional roller clutch with an unlocking mechanism is configured as shown in FIGS. An outer ring 2 is provided around an inner cylinder 1 serving as an inner member via a sliding bearing 3.
The outer ring 2 is rotatably supported.
Is externally fixed. The gear 4 is for transmitting the movement of a separately provided operating handle or the like to the outer ring 2.
A cam ring 5 is externally fitted and fixed to the outer peripheral surface of the intermediate portion of the inner cylinder 1. The cam ring 5 is opposed to a portion of the outer ring 2 on the inner peripheral surface at one end (the right end in FIG. 5) that is separated from the slide bearing 3.

A cam gap 6 is formed between the outer peripheral surface of the cam ring 5 and the inner peripheral surface of the outer ring 2 so that the clearance dimension in the diameter direction varies in the circumferential direction. And
A plurality of rollers 7 are rotatably inserted into the cam gap 6. Further, compression springs 9, 9 as lock urging means are provided between the step portions 8, 8 formed on the outer peripheral surface of the cam ring 5 and the rollers 7, 7, respectively. Pressing in the same direction on the circumference.

On the outer peripheral surface of the inner cylinder 1, the cam ring 5
A rotatable ring 10 is rotatably supported at a portion adjacent to the rotary ring 10 via a slide bearing 11. This rotating ring 10
, A plurality of pressing pins 12, 12 constituting a protruding piece,
Each pressing pin 1 is supported at substantially equal intervals in the circumferential direction.
One half (12, 12) (left half in FIG. 5) is projected from one side surface (left side in FIG. 5) of the rotating ring 10. One half of each of the pressing pins 12, 12 enters the cam gap 6, and faces the rollers 7, 7 from the side opposite to the compression springs 9, 9.

Further, the other side of the rotating ring 10 (FIG. 5)
The right end surface of the lock pin 13 has a base end fixed thereto. The tip of the locking pin 13 and the inner cylinder 1
A tension spring 15 is provided between the lock pin 14 and another locking pin 14 fixedly provided on the outer peripheral surface of the cover. The tension spring 15 gives the rotating ring 10 an elastic force in the same direction as the compression springs 9 press the rollers 7.

In the conventional roller clutch with an unlocking mechanism constructed as described above, when the rotation of the inner cylinder 1 is free inside the outer ring 2, the rotation ring is opposed to the tension spring 15. 10 is rotated clockwise in FIG.
With the rotation of the rotating ring 10, each of the pressing pins 12,
12 pushes each roller 7, 7 against the elasticity of the compression springs 9, 9. As a result, each roller 7, 7 remains in a state of being moved to a part of the cam gap 6 where the gap dimension in the diametrical direction is increased. Therefore, the rollers 7, 7 do not bite into the cam gap 6, and the inner cylinder 1 can freely rotate inside the outer ring 2 regardless of the existence of the outer ring 2.

On the other hand, when transmitting the movement of the outer race 2 to the inner cylinder 1, the rotary ring 10 is rotated based on the elasticity of the tension spring 15, and as shown in FIG. And the rollers 7 are separated from each other. In this state, if the outer ring 2 is rotated counterclockwise in FIGS.
Each of the rollers 7, 7 is provided by the elasticity of the compression springs 9, 9 and the outer ring 2
7 moves counterclockwise in FIG. 7 based on the frictional force with the inner peripheral surface, and bites into a part of the cam gap 6. As a result, the movement of the outer ring 2 is transmitted to the inner cylinder 1 via the rollers 7, 7 and the cam ring 5.

When the outer ring 2 is rotated in the clockwise direction in FIGS. 6 to 7 in the above state, the direction in which the rollers 7, 7 move with the rotation of the outer ring 2 and the compression spring 9, 9
However, the directions in which the rollers 7, 7 are moved are opposite to each other, and the rollers 7, 7 tend to move away from the portion where the width of the cam gap 6 is reduced. Therefore, each roller 7, 7
Can be rolled in the cam gap 6 between the inner peripheral surface of the outer ring 2 and the outer peripheral surface of the cam ring 5, and the relative rotation between the outer ring 2 and the inner cylinder 1 becomes free, so that the outer ring 2 Rotating force is inner cylinder 1
Will not be transmitted. When the inner cylinder 1 tends to rotate clockwise in FIG. 7 in the above state, the cam rings 5 try to rotate clockwise in FIG. Based on the elasticity of the cam ring 5 and the frictional force between the cam ring 5 and the cam ring 6.
As a result, the relative rotation between the outer race 2 and the inner cylinder 1 becomes impossible, and the inner cylinder 1 rotates based on the rotation of the outer race 2.

[0010]

The roller clutch with an unlocking mechanism according to the present invention prevents an excessive force from acting on each of the constituent members when the roller is pressed to release the lock. The purpose is to prevent damage to the members. In the case of the conventional structure shown in FIGS.
When the lock state is released, the force applied to the rotating ring 10 is directly applied to the rollers 7 via the pins 12. At the moment when the rollers 7, 7 in the stationary state are started to move into the cam gap 6, a relatively large force is required, but a force larger than the required force is applied to the pins 12, 12. In this case, this pin 12, 1
2 may be damaged.

As a conventional roller clutch, there is also known one having a structure in which the lock direction can be freely changed as described in, for example, Japanese Patent Application Laid-Open No. 55-163330. In the case of the structure described in this publication, the lock can be released, but it still has the same problem. The roller clutch with a lock release mechanism of the present invention has been devised in view of the above-described circumstances.

[0012]

A roller clutch with an unlocking mechanism according to the present invention has a cylindrical outer ring and, inside the outer ring, concentrically with the outer ring, similarly to the roller clutch with a conventional unlocking mechanism described above. An inserted inner member, a cam gap provided between the outer peripheral surface of the inner member and the inner peripheral surface of the outer ring, and having a radially varying gap dimension in the circumferential direction; A plurality of rollers inserted therein, a lock biasing means for pressing each roller in the same circumferential direction, and a portion axially displaced from the roller, concentrically with the outer ring and the inner member and these outer rings and A rotating ring supported so as to be freely displaceable in the rotational direction with respect to the inner member,
The same number of projecting pieces as the number of the rollers, which are provided on one side surface of the rotating ring at substantially equal intervals in the circumferential direction, and each of the plurality of rollers faces the opposite side to the lock urging means; The rotation ring includes a return urging unit that applies an elastic force in the same direction as the lock urging unit presses each roller.

In particular, in the roller clutch with an unlocking mechanism according to the present invention, a releasing ring supported around the rotating ring concentrically with the rotating ring and rotatably supported by the rotating ring; And a release urging means provided between the rotating ring and the rotating ring, the elastic urging force having an elastic urging force against a total urging force of the urging force of the lock urging means and the urging force of the return urging means. . Then, with the rotation of the release ring, the rotation ring is rotated via the release urging means, and a plurality of protruding pieces provided on the rotation ring respectively cause the elasticity of the lock urging means to rotate the roller. It is configured to press against the pressure.

[0014]

The operation of the roller clutch with an unlocking mechanism according to the present invention constructed as described above is as follows. When the inner member is to be freely rotated while the outer ring is stationary, the release ring is rotated. As the rotating ring is rotated in this manner, each projection pushes each roller against the elasticity of the lock urging means. As a result, each roller
A part of the cam gap remains in a state where it has moved to a part where the gap dimension in the diametrical direction has increased. Therefore, the rollers do not bite into the cam gap, and the inner member can freely rotate inside the outer ring even though the outer ring is stationary.

As described above, when the roller is pressed by each protruding piece in order to release the lock, the force applied to the release ring is not transmitted to each protruding piece as it is, but via the release urging means. Is transmitted. Then, at the moment when the elasticity based on the deformation of the release urging means exceeds the force required to move the rollers, each roller is directed toward the portion where the clearance dimension in the diametrical direction is increased in the cam clearance. Moving. Therefore, when unlocking is performed,
Excessive force can be prevented from being applied.

When the movement of the outer ring is transmitted to the inner member, the rotating ring is rotated based on the elasticity of the return urging means to separate the projection from the roller. When the outer ring is rotated in a predetermined direction in this state, the rollers move based on the elastic force of the lock urging means and the frictional force between the inner peripheral surface of the outer ring and bite into a part of the cam gap. As a result, the movement of the outer ring is transmitted to the inner member via each roller.
When the outer ring rotates in a direction opposite to the predetermined direction, the direction in which each roller tries to move with the rotation of the outer ring and the direction in which the lock urging means tries to move each roller are opposite to each other. And each roller tends to move away from the portion where the width of the cam gap is reduced. For this reason, each roller can roll in the cam gap, and the relative rotation between the outer ring and the inner member is free, so that the rotational force of the outer ring is not transmitted to the inner member. If the inner member tends to rotate in the same direction as the urging direction of the lock urging means even though the outer race is stationary, the rollers are adjusted to the elasticity of the lock urging means and the outer periphery of the inner member. Based on the frictional force with the surface,
Cut into a part of the cam gap. As a result, the inner member does not rotate.

[0017]

1 to 3 show a first embodiment of the present invention. A cylindrical outer ring 17 made of a material having sufficient rigidity and hardness, such as bearing steel, is held on the inner peripheral surface of the housing 16 made of a synthetic resin such that the outer ring 17 cannot rotate with respect to the housing 16. The inner circumferential surface of the outer ring 17 is a polygonal cylindrical cam surface 20 in which a plurality of flat portions 18 and 18 and arc portions 19 and 19 are alternately continuous. Inside the outer ring 17, a cylindrical inner ring 21 as an inner member is provided.
It is inserted concentrically with the outer ring 17. Accordingly, a cam gap 22 is formed between the outer peripheral surface of the inner race 21 and the inner peripheral surface of the outer race 17 so that the clearance dimension in the diameter direction changes in the circumferential direction. A plurality of rollers 23, 23 are inserted into the cam gap 22.

The rollers 23 are rotatably held in the cam gap 22 by a cage 24 made of synthetic resin. That is, the retainer 24 connects the pair of rim portions 25 and 26 located at intervals with each other to the plurality of connecting portions 2.
It is configured by connecting at 7, 28. Then, the pocket 4 existing between the adjacent connecting portions 27 and 28 is formed.
Each of the rollers 23, 23 is rotatably held on each of the rollers 6, 46. Also, one of the connecting portions 28, 2
8 supports leaf springs 29, 29 as lock urging means.
3, 23 are pressed counterclockwise in FIGS.

In the illustrated embodiment, the outer diameter of one of the rims 25 constituting the retainer 24 is determined by changing the outer diameter of the outer race 1.
7 is larger than the inside diameter. And this rim part 2
5 is sandwiched between one end surface (the left end surface in FIG. 2) of the outer race 17 and a flange portion 30 formed on the inner peripheral edge of the opening of the housing 16. Therefore, the above cage 2
4 does not shift with respect to the outer ring 17 in the axial direction. Further, the other rim portion 26 has an outer peripheral edge shape that matches the inner peripheral surface of the outer ring 17. Therefore, the rim 26 is connected to the outer race 17.
The rotation of the retainer 24 with respect to the outer ring 17 is prevented in a state where the retainer 24 is fitted inside the other end (the right end in FIG. 2).

A rotatable ring 31 formed by press-forming a metal plate having sufficient rigidity is rotatably supported at a portion inside the other end of the outer ring 17 and separated from the retainer 24. I have. On one side surface (left side surface in FIG. 2) of the rotating ring 31, a part of the metal plate is bent,
The same number of protrusions 32, 32 as the rollers 23, 23 are provided at equal intervals in the circumferential direction. Each of these projections 32,
Reference numeral 32 is parallel to the rollers 23, 23.

On the other hand, the rim 2 constituting the retainer 24
In a part of the part 6 which faces each of the protruding pieces 32, there are formed through holes 33, 33 which are long in the circumferential direction, respectively. In addition, a part of the connection portion 27, each of the through holes 33,
Recesses 34, 34 are formed at positions matching with 33. With the rotating ring 31 being fitted inside the other end of the outer race 17, the projecting pieces 32, 32
3, and is inserted into each of the recesses 34, 34 and faces one side of the plurality of rollers 23, 23, respectively.

Further, by bending a part of the metal plate constituting the rotating ring 31 outward in the diametrical direction, the locking arm 3 is formed.
5 are formed. The tip of the locking arm 35 projects diametrically outward from the outer peripheral surfaces of the rotating ring 31 and the outer ring 17. A tension spring 36 is provided between the intermediate portion of the locking arm 35 and the side surface of the housing 16 as return biasing means. This tension spring 3
6 is connected to the rotating ring 31 via the locking arm 35,
In FIG. 1, the elasticity in the counterclockwise direction is given,
2 and each roller 23, 23 tend to separate from each other.

Further, a release ring 37 made of, for example, a synthetic resin is supported around the rotation ring 31 so as to be concentric with the rotation ring 31 and rotatable with respect to the rotation ring 31. That is, the housing 16
The release ring 3 is inserted into an annular concave portion 38 opened on the side surface of the
7 is rotatably fitted. At the end of the release ring 37, a pressing plate portion 39 is formed on an inner peripheral surface of a portion protruding from the concave portion 38 and positioned around the locking arm 35. Further, a compression spring 40 serving as a release urging means is provided between the pressing plate portion 39 and the locking arm 35. When the release ring 37 is rotated clockwise in FIG.
6 has a sufficient elasticity to rotate the locking arm 35 by a predetermined amount against the total elasticity of the elasticity of the plurality of leaf springs 29, 29, and preferably has an elasticity larger than the total elasticity. In addition, the locking arm 35 is provided on the same side as the extension spring 36.

A through hole 41 having a circular cross section is formed in a part of the housing 16 in the axial direction of the housing 16. The pressing plate 39 faces one half (the right half in FIG. 1) of one end (the right end in FIG. 2) of the through hole 41. Rotation holding means for rotatably inserting the shaft 42 into the through hole 41 and holding the release ring 37 rotated by a predetermined angle against the elasticity of the tension spring 36 constitutes. ing. That is, the tip of the shaft 42 (the right end in FIG. 2).
Is a semi-cylindrical cam portion 43, and the outer peripheral surface of the cam portion 43 and one surface of the pressing plate portion 39 can be freely abutted.
Further, a knob 44 is fixed to the base end of the shaft 42 so that the shaft 42 can be rotated by fingers. The position at which such a shaft 42 is provided and the shape of the cam portion 43 are such that when the release ring 37 rotates with the rotation of the cam portion 43, the compression spring 40 pushes the locking arm 35, The plurality of projecting pieces 32 provided on the rotating ring 31 are determined so as to press the rollers 23 against the elasticity of the leaf springs 29 respectively.

When the roller clutch with the unlocking mechanism of the present invention constructed as described above is incorporated into a fishing reel, for example, the reel for winding the fishing line and the inner ring 21 are rotatable in synchronization with each other, and the housing 16 is rotated. Is rotatably driven by a handle operated by the angler. When the inner ring 21 is freely rotated to send out the yarn from the reel in the assembled state, the knob 44 is operated to displace the cam portion 43 at the tip of the shaft 42 to the chain line state in FIG. Then, the release ring 37 is slightly rotated clockwise in FIG.

With the rotation of the release ring 37, the pressing plate portion 39 presses the compression spring 40, and the locking arm 35 is displaced against the elasticity of the tension spring 36, so that the rotation ring 31 is rotated as shown in FIG. Rotated in the direction. In this way, the rotating ring 3
As the 1 is rotated, each protruding piece 32, 32 pushes each roller 23, 23 in the clockwise direction in FIG. 1 against the elasticity of the leaf springs 29, 29. As a result, each roller 23, 2
3 remains in a state where it has moved to a portion of the cam gap 22 where the dimension of the gap in the diametrical direction has increased. Therefore, the rollers 23, 23 do not bite into the narrowed portion of the cam gap 22, and the inner ring 21 is rotated counterclockwise inside the outer ring 17 although the housing 16 and the outer ring 17 are stationary. Will be able to rotate freely.

As described above, in order to release the lock, each projection 3
When the rollers 23, 23 are pressed by the rollers 2, 32, the force applied to the release ring 37 from the cam portion 43 of the shaft 42 is not transmitted to the respective projecting pieces 32, 32 as it is, but via the compression spring 40. Is transmitted. And this compression spring 40
At the moment when the elasticity based on the deformation of the roller 23 exceeds the force required for moving the rollers 23, 23, each roller 23, 23 is directed toward the portion of the cam gap 22 where the gap size in the diametrical direction is increased. Moving. Therefore, when unlocking is performed, it is possible to prevent an excessive force from being applied to the abutting portions between the protruding pieces 32, 32 and the rollers 23, 23.

When transmitting the movement of the outer ring 17 to the inner ring 21 such as when catching a fish caught on a needle, the knob 4 is used.
Based on the operation of No. 4, the cam portion 43 is set in a state shown by a solid line in FIG. In this state, the compression spring 40 does not strongly press the locking arm 35, and the rotating ring 31 is positioned as shown in FIG. 1 by the elastic force of the extension spring 36. In this state, the protruding pieces 32, 32 and the rollers 23, 23 are separated from each other. In this state, the housing 16 and the outer race 17 are operated based on the operation of the handle.
Is rotated clockwise in FIG.
3 and 23 move based on the elasticity of the leaf springs 29 and 29 and the frictional force between the inner peripheral surface of the outer ring 17 and bite into a part of the cam gap 22. As a result, the movement of the outer ring 17 is
It is transmitted to the inner race 21 via 3 and 23, and rotates the reel in the fishing line winding direction. When the outer race 17 rotates counterclockwise in FIG. 1, each roller 23, 23 tends to move away from the portion where the width of the cam gap 22 is reduced. For this reason, the rollers 23, 23 can be rolled in the cam gap 22, the relative rotation between the outer ring 17 and the inner ring 21 is free, and the rotational force of the outer ring 17 is not transmitted to the inner ring 21. .

When the handle is not operated, and therefore the inner line 21 tends to rotate in the counterclockwise direction in FIG. 1 due to the fishing line being pulled in spite of the fact that the housing 16 and the outer ring 17 are stationary. Is the roller 2
3 and 23 bite into a part of the cam gap 22 based on the elasticity of the leaf springs 29 and 29 and the frictional force between the outer peripheral surface of the inner ring 21.
As a result, the inner ring 21 does not rotate. Therefore, the fishing line is not pulled out from the reel without holding the handle.

FIG. 4 shows a second embodiment of the present invention. In the case of the present embodiment, as a return urging means for applying elasticity in the unlocking direction to the rotating ring 31,
A compression spring 45 is used. It is needless to say that the elasticity of the compression spring 45 is preferably smaller than the elasticity of the compression spring 40 as the release urging means. Other configurations and operations are the same as those of the first embodiment described above,
Equivalent portions are denoted by the same reference numerals, and redundant description will be omitted.

The return urging means and the cancel urging means are as follows.
The present invention is not limited to the illustrated compression spring and tension spring, but may be a torsion coil spring, a leaf spring, rubber (urethane rubber), or resin. Also, the lock urging means for pressing the rollers 23, 23 may be a compression coil spring, rubber (urethane rubber), or a spring integrated with a resin retainer. Further, in the above-described embodiment, the cam gap 22 is
Outer ring 1 which is a cylindrical outer peripheral surface of inner ring 21 and cam surface 20
7, the outer peripheral surface of the inner ring 21 is a polygonal cylindrical cam surface, and the inner peripheral surface of the outer ring 17 is a cylindrical surface. As a shape, the cam gap 22 may be formed by the inner and outer peripheral surfaces.

The rotation holding means may have another structure such as a push button type. That is, as shown in FIG. 8, the large-diameter portion 4 of the button guide 49 including a large-diameter portion 47 at one end (left end in FIG. 8) and a rod 48 at the other end (right end in FIG. 8).
7 is loosely fitted to the push button 50, and the male screw 51 formed at the tip of the rod 48 is screwed into the screw hole 52 provided in the locking arm 35. A compression spring 53 is provided between the locking arm 35 and the peripheral edge of the opening of the push button 50 as a release urging means. Other configurations are similar to those of the first and second embodiments.

With the above configuration, the push button 5
When 0 is pressed, the locking arm 35 is pressed clockwise in FIG. 8 via the compression spring 53, and the lock is released in the same manner as in the first and second embodiments. A conventionally known mechanism, such as incorporating an alternate mechanism, may be used as the rotation holding means, or the push button 50 may be continuously pressed by a finger. When transmitting the movement of the outer ring to the inner ring, if the pressing of the push button 50 is released, the tension spring 36 (FIG. 1)
Alternatively, the rotating ring 31 rotates counterclockwise in FIG. 8 based on the elastic force of the compression spring 45 (FIG. 4), and operates in the same manner as in the first and second embodiments. 2

[0034]

The roller clutch with the unlocking mechanism according to the present invention is constructed and operates as described above, so that excessive force is prevented from being applied to each of the constituent members, thereby preventing breakage of these members. , Durability and reliability can be improved.

[Brief description of the drawings]

FIG. 1 is a partial side view showing a first embodiment of the present invention.

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

FIG. 3 is a sectional view taken along line BB of FIG. 2;

FIG. 4 is a partial side view showing a second embodiment of the present invention.

FIG. 5 is a sectional view showing an example of a conventional structure.

FIG. 6 is a side view of FIG. 5;

FIG. 7 is a sectional view taken along line CC of FIG. 5;

FIG. 8 is a side view of an essential part showing an example in which both the release urging means and the return urging means are used, with a part thereof being cut longitudinally;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Inner cylinder 2 Outer ring 3 Sliding bearing 4 Gear 5 Cam ring 6 Cam gap 7 Roller 8 Step 9 Compression spring 10 Rotating ring 11 Sliding bearing 12 Pressing pin 13, 14 Lock pin 15 Tension spring 16 Housing 17 Outer ring 18 Flat part 19 Arc Part 20 cam surface 21 inner ring 22 cam gap 23 roller 24 retainer 25, 26 rim part 27, 28 connecting part 29 leaf spring 30 flange part 31 rotating ring 32 protruding piece 33 through hole 34 concave part 35 locking arm 36 tension spring 37 release Ring 38 Concave portion 39 Press plate portion 40 Compression spring 41 Through hole 42 Shaft 43 Cam portion 44 Knob 45 Compression spring 46 Pocket 47 Large diameter portion 48 Rod 49 Button guide 50 Push button 51 Male screw portion 52 Screw hole 53 Compression spring

Claims (2)

(57) [Scope of request for utility model registration] 1. A cylindrical outer ring, an inner member inserted concentrically with the outer ring inside the outer ring, and provided between an outer peripheral surface of the inner member and an inner peripheral surface of the outer ring in a diametrical direction. A cam gap in which the gap dimension over the circumference varies in the circumferential direction;
A plurality of rollers inserted into the cam gap, a lock urging means for pressing each roller in the same circumferential direction, and a portion axially displaced from the roller, concentric with the outer ring and the inner member and A rotating ring supported so as to be freely displaceable in the rotating direction with respect to the outer ring and the inner member; and a plurality of rollers each of which is provided on one side surface of the rotating ring at substantially equal intervals in a circumferential direction. Opposite to the lock urging means, the same number of protrusions as the rollers, and return urging means for applying elasticity in the same direction as the lock urging means pressing each roller to the rotating ring; In the roller clutch with a lock release mechanism provided with a release ring, the release ring is supported around the rotation ring concentrically with the rotation ring and rotatably supported by the rotation ring; Provided between the ring, the
The urging force of the lock urging means and the return urging means
A release biasing means having a resilient biasing force against the biasing force which is the sum of the biasing force, and with the rotation of the release ring to rotate the rotating ring through the release biasing means, this a plurality of projecting pieces provided on the rotary ring, on each
A roller clutch with an unlocking mechanism, wherein the roller is pressed against the elasticity of the lock urging means. 2. The roller clutch with an unlocking mechanism according to claim 1, further comprising rotation holding means for holding the release ring rotated by a predetermined angle against the elasticity of the return urging means.