JPH09229096A - One-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stabilize behavior of a roller, prevent the roller from colliding with lock recessed parts provided on an inner at overrun, and engage the roller with the lock recessed part so as to surely transmit power at power transmis sion. SOLUTION: This one-way clutch is formed with lock recessed parts 34a for locking with a roller 37 on the outer circumferential face of an inner 34 coaxially arranged on the inner circumference of an outer 36, and annular grooves 34b for receiving energization rings 40 on both end parts in the axial direction of the inner 34 in the circumferential direction so as to cross with the lock recessed parts 34a. The energization ring 40 is provided capably of being elastically deformed in the radial direction, and the outer circumferential face is positioned between the deepest part B and the topmost part C of the lock recessed parts 34a in the radial direction. The energization ring 40 has fixed width in the lengthwise direction of the roller 37, about a half of the width is protruded outside from the end face of the roller 37, and the outer circumferential face of the protruded part position is fitted to the inner circumferential face of the outer side wall part and the inner circumferential face of a plate.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a one-way clutch used in a starter for starting an engine.

[0002]

2. Description of the Related Art In a one-way clutch used for a starter, a cam chamber formed by an outer and an inner is filled with a lubricant in order to smoothly operate the clutch. However, if a lubricant with an extremely low coefficient of friction is used, slippage will occur between the roller housed in the cam chamber and the inner,
Torque cannot be transmitted. Further, when a lubricant having a large friction coefficient is used, the outer peripheral surface of the inner and the outer peripheral surface of the roller are worn at the time of overrun, which may cause a problem in the durability of the clutch. Therefore, the applicant of the present application has proposed a one-way clutch that has little influence on friction (Japanese Patent Application No. 6-213707). As shown in FIG. 8, this one-way clutch has a locking recess 110 formed on the outer peripheral surface of the inner 100.
The torque is transmitted while the roller 120 is locked.

Further, in this one-way clutch, an annular groove 130 along the circumferential direction is provided on the outer peripheral portion of the inner 100 in order to promote the separation of the roller 120 from the locking recess 110 at the time of overrun. An annular elastic body 140 is stored in 130. The elastic body 140 receives the centrifugal force generated by the rotation of the inner 100 and is deformed in the centrifugal direction, thereby pressing the roller 120 and helping the roller 120 to separate from the locking recess 110.

[0004]

However, in the one-way clutch of the prior application, the center of the elastic body 140 does not always become concentric with the inner 100 when the elastic body 140 is deformed in the centrifugal direction by the centrifugal force. It may be eccentric to the center of rotation of the inner 100. Therefore, the elastic body 14
The contact between the roller 0 and the roller 120 becomes irregular, and the roller 12
Since the outer 150 is also irregularly shaken as the behavior of 0 becomes unstable, it is difficult to stably maintain the overrun performance. In addition, the annular elastic body 140 has the inner 100
If the rollers 120 are not concentric with each other, the roller 120 cannot be held in a perfect circle on the outer periphery of the inner 100, and thus the intermittent contact between the locking recess 110 of the inner 100 and the roller 120 occurs.
As a result, the roller 120 is hit by the locking recess 110, so that the roller 120 and the locking recess 110 collide with each other and are deformed, or a collision noise is generated by the collision. Alternatively, due to unstable behavior of the roller 120, the roller 12
Problems such as repeated fatigue of the spring 160 that biases 0 occur.

The number of revolutions of the inner 100 driven by the engine at the time of overrun is irregular depending on the model and state of the engine, and if the elastic body 140 is set to be deformed at a low speed, the inner 100 will be rotated at a high speed. The elastic body 140 is easily deformed and is likely to be damaged. On the other hand, elastic body 1
If 40 is set to be deformed at high rotation, the inner 100
Of the roller 1 when the rotation speed of the roller 1 is low, the elastic body 140 cannot be completely deformed.
20 and the locking recess 110 collide with each other, and the above-described problem occurs. The present invention has been made based on the above circumstances, and an object thereof is to stabilize the behavior of a roller and
It is an object of the present invention to provide a one-way clutch that prevents collision between a roller and a locking recess during overrun, and engages the roller with the locking recess during power transmission to ensure reliable power transmission.

[0006]

According to the invention of claim 1, since the annular elastic body is housed in the groove portion so that the outer peripheral surface is located between the deepest portion and the top portion of the locking recess, It is possible to reduce collision resistance or catching resistance between the roller and the locking recess when the outer and the inner run idle. This allows
Since the idling performance is improved and the behavior of the roller is stable, it is possible to prevent deformation due to the collision between the roller and the locking concave portion, and it is possible to prevent repeated fatigue of the urging member for urging the roller in the accommodation chamber. In addition, since the annular elastic body urges the roller to separate from the locking recess by the elastic force when the inner and outer parts are overrun, the contact resistance between the inner and outer parts is reduced and the friction noise at the time of overrun is reduced. It is possible to reduce the noise.

According to the second aspect of the invention, since the annular elastic body is in contact with the roller at both ends in the longitudinal direction of the roller,
It is possible to prevent the roller from tilting and obtain stable behavior.

According to the third aspect of the invention, since the outer peripheral surface of the annular elastic body is regulated by the outer or plate, it is possible to limit centrifugal deformation of the annular elastic body to the range where the function of the clutch can be secured. Become. Further, since the annular elastic body is centered on the outer or the plate, it is possible to hold the rollers in the accommodation chamber of the outer at a uniform position, and the outer and the inner can be coaxial with each other during overrun. Furthermore, since the outer peripheral surface of the annular elastic body is regulated by the outer or plate, the outer side has a starter no-load rotation compared to the inner side, which is rotated at a high rotation speed by the engine during overrun, so the influence of centrifugal force is reduced. It is possible to reduce the abnormal deformation of the annular elastic body.

According to the fourth aspect of the present invention, since the annular elastic body is set so as not to be deformed by the urging force of the urging member, the function of the annular elastic body (the elastic force for urging the roller toward the outer periphery) at the time of overrun is impaired. It is possible to surely disengage the roller from the locking recess without being damaged.

According to the fifth aspect of the present invention, since the outer peripheral surface of the annular elastic body is set to have substantially the same diameter as the top of the locking recess, the roller and the locking recess when the outer and inner wheels run idle. There is no collision or getting caught. As a result, the idling performance is improved and the behavior of the roller is stabilized, so that it is possible to prevent deformation due to the collision between the roller and the locking recess, and to prevent repeated fatigue of the urging member that urges the roller in the storage chamber. . In addition, since the annular elastic body urges the roller to separate from the locking recess by the elastic force when the inner and outer parts are overrun, the contact resistance between the inner and outer parts is reduced and the friction noise at the time of overrun is reduced. It is possible to reduce the noise. In addition, since the annular elastic body is a thin annular ring without interruption, it has strength despite its small weight, and the annular elastic body does not undergo centrifugal deformation even when subjected to centrifugal force, and is limited to the range where the clutch function can be secured. It becomes possible to do. In addition, since the other end of the annular elastic body is fixed to the inner member and centered, it is possible to hold the rollers in the outer accommodation chamber at even positions, and it is possible to obtain coaxiality between the outer member and the inner member during overrun. it can.

According to the invention of claim 6, since the annular elastic body is in contact with the roller at both ends in the longitudinal direction of the roller,
It is possible to prevent the roller from tilting and obtain stable behavior.

According to the invention of claim 7, even if the annular elastic body is deformed by the urging force of the urging member, the outer diameter at one end is set to be equal to or larger than the topmost diameter of the locking recess, so that the annular elastic body is provided at the time of overrun. It is possible to reliably disengage the roller from the locking recess without impairing the function of the body (elastic force that biases the roller to the outer periphery).

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of a starter having a one-way clutch of the present invention will be described with reference to the drawings. (First Embodiment) FIG. 1 is a sectional view of a one-way clutch.
As shown in FIG. 3, the starter 1 includes a starter motor 2 that generates a rotational force when energized, a planetary gear speed reducer (described later) that reduces the rotation of the starter motor 2 and transmits the rotation to the output shaft 3, a starter. 1, a shock absorber (which will be described later) that absorbs excessive torque applied to the drive system, a pinion gear 4 that is fitted to the output shaft 3, a one-way clutch 5 that transmits the rotation transmitted to the output shaft 3 to the pinion gear 4, and a pinion gear 4. And a magnet switch 6 for controlling the energization of the starting motor 2 and the like.

The starting motor 2 is a well-known DC motor, and both ends of the shaft 7 are connected to the output shaft 3 via bearings 8 and 9.
, An armature 11 rotatably supported by the end frame 10, a fixed magnetic pole (a pole core 12 and a field coil 13) arranged on the outer periphery of the armature 11, and a cylindrical yoke 14 holding the fixed magnetic pole on the inner peripheral surface. The brush 16 and the like are in sliding contact with the commutator 15 provided on the outer periphery of the rear end of the shaft 7. A permanent magnet may be used as the fixed magnetic pole.

The output shaft 3 is arranged in front of the armature 11 coaxially with the shaft 7, and has a bearing 17 fitted to the outer circumference of the tip.
And a bearing 18 fitted to the outer periphery near the rear end, and rotatably supported by the front end of the front housing 19 and the inner cylindrical portion 20a of the center bearing 20. A hollow cylindrical recess is formed at the center of the rear end of the output shaft 3, and the tip of the shaft 7 is rotatably supported in the recess via the bearing 8. A stop collar 21 for restricting the forward movement of the pinion gear 4 is provided on the outer periphery of the output shaft 3 near the tip.
Is attached. The stop collar 21 is restricted from moving forward in the axial direction via a snap ring 22 that fits in a circumferential groove 3a formed on the outer circumference of the output shaft 3.

The planetary gear reduction device includes a sun gear 23 formed on the outer periphery of the tip of the shaft 7, a plurality of planet gears 24 meshing with the sun gear 23, an internal gear 25 meshing with each planet gear 24, and a rear end of the output shaft 3. It is composed of the planet carrier 26 provided in the. Sun gear 2
3 rotates integrally with the shaft 7 to rotate and drive each planetary gear 24. Each planetary gear 24 is rotatably supported by a pin 27 press-fitted into a planet carrier 26 via a bearing 28, and receives the rotation of the sun gear 23 and revolves around the outer periphery of the sun gear 23 while rotating. The internal gear 25 is engaged with a friction plate 29 of the shock absorber, and the movement of the internal gear 25 in the rotational direction is restricted by the friction plate 29. The planet carrier 26 rotates together with the revolution of each planetary gear 24 and generates a rotational force on the output shaft 3.

The shock absorber comprises the above-mentioned friction plate 29, washer 30, disc spring 31, adjusting screw 32 and the like. The friction plate 29 receives the disc spring 3 via the washer 30.
It receives the urging force of 1 and is frictionally engaged with the center bearing 20. The adjusting screw 32 is screwed to the male screw portion 20b formed on the outer periphery of the inner cylindrical portion 20a of the center bearing 20 to adjust the biasing force of the disc spring 31 that biases the friction plate 29. In this shock absorber, when an excessive torque exceeding the static torque generated by the frictional engagement force between the center bearing 20 and the friction plate 29 is applied, the friction plate 29 rotates with respect to the center bearing 20 to rotate the internal gear 25. Therefore, excessive torque can be absorbed. Of course, the internal gear 25 may be held non-rotatably with the fixed member (for example, the center bearing 20) without the shock absorber.

The pinion gear 4 meshes with the ring gear 33 of the engine to apply the rotational force of the starting motor 2 to the ring gear 3.
3 is provided integrally with the inner 34 of the one-way clutch 5 and is fitted to the outer periphery of the output shaft 3 via the bearing 35. The one-way clutch 5 includes an outer 36, an inner 34, a roller 37, a spring 38 (see FIG. 1), a plate 39, a biasing ring 40 (annular elastic body of the present invention / see FIG. 1), a clutch cover 41, and the like. To be done. The outer 36 has a helical spline 42 on the output shaft 3.
Is formed integrally with the spline tube 43 which is fitted via the through hole, and a wedge-shaped cam chamber 36a (the accommodating chamber of the present invention / see FIG. 1) for accommodating the roller 37 and the spring 38 is formed on the inner peripheral surface thereof. . This cam chamber 36a is
6 A plurality of inner circumferential surfaces are provided at equal intervals in the circumferential direction.

The inner member 34 is coaxially arranged on the inner periphery of the outer member 36 on the rear side of the pinion gear 4. This inner 3
A locking recess 34a (see FIG. 1) for locking the roller 37 during torque transmission is formed on the outer peripheral surface of the roller 4.
The plurality of locking recesses 34a are provided at equal intervals in the circumferential direction of the outer peripheral surface of the inner 34 (for example, an integral multiple of the cam chamber 36a). Further, annular groove portions 34b (see FIG. 1) for accommodating the urging ring 40 are formed at both axial end portions of the inner 34 so as to intersect with the respective locking recesses 34a in the circumferential direction.
The groove 34b is formed deeper than the locking recess 34a by the thickness of the biasing ring 40 or more.

The roller 37 is provided in a cylindrical shape, and when the torque for transmitting the rotation of the outer 36 to the inner 34 is transmitted, the roller 37 moves to a narrower side of the cam chamber 36a and engages with the outer 36 and the inner 34, so that the outer 37 The rotation of 36 is transmitted to the inner 34. Further, the rotation speed of the inner 34 becomes higher than that of the outer 36 after the engine is started (overrun).
Then, the roller 37 moves to the wider side of the cam chamber 36a, disengages from the locking recess 34a, and disengages from the outer 36 and the inner 34, so that the rotation of the inner 34 is transmitted to the outer 36. Can be prevented. The spring 38 is arranged in each cam chamber 36a together with the roller 37, and biases the roller 37 toward the narrow side of the cam chamber 36a.

As shown in FIG. 4, the plate 39 is arranged on the opposite side of the side wall portion 36b of the outer 36 in the longitudinal direction of the roller 37, and restricts the axial movement of the roller 37 together with the side wall portion 36b of the outer 36. doing. Biasing ring 40
Is stored in the groove 34b provided in the inner 34,
It is provided so as to be elastically deformable in the radial direction. However, it is set so as not to be deformed by the biasing force of the spring 38 that biases the roller 37. As shown in FIG. 1, the biasing ring 40 is sized so that the outer peripheral surface thereof is located between the deepest portion B and the top portion C of the locking recess 34a in the radial direction. Further, the biasing ring 40 has a predetermined width in the longitudinal direction of the roller 37 (left-right direction in FIG. 4), and about half of the width direction thereof protrudes outward from the end surface of the roller 37, and in a stationary state. The outer peripheral surface of the protruding portion is the inner peripheral surface of the side wall portion 36b of the outer 36 and the plate 39.
It is housed in the groove 34b in a state of being fitted to the inner peripheral surface of the. The clutch cover 41 covers the outer periphery of the outer 36 and fixes the outer 36 and the plate 39.

When the starter switch is turned on, the magnet switch 6 energizes a built-in coil (not shown) to generate a magnetic force, so that a plunger (not shown) arranged inside the coil is provided. The motor contact is attracted to close the motor contact, and the lever 44 is driven by the plunger attraction force. The lever 44 has one end engaged with a joint 45 connected to the plunger and the other end engaged with the outer circumference of the spline tube 43 so as to be swingable around a fulcrum 46 provided in the front housing 19. ing.

Next, the operation of this embodiment will be described. When the coil in the magnet switch 6 is energized and the plunger is attracted by the ON operation of the starter switch, the lever 44 engaging with the joint 45 swings around the fulcrum 46. As a result, the spline tube 43 connected to the other end of the lever 44 is pushed forward on the output shaft 3 along the helical spline 42, so that the pinion gear 4 moves forward on the output shaft 3 together with the one-way clutch 5.

On the other hand, when the motor contact in the magnet switch 6 is closed, a current flows from the battery to the starting motor 2 to generate a rotational force in the armature 11, and the armature 1
The rotation of No. 1 is reduced by the reduction gear and transmitted to the output shaft 3. The rotation of the output shaft 3 is transmitted to the outer 36 via the spline tube 43 to rotate the outer 36. When the outer 36 rotates, the relative rotation between the outer 36 and the inner 34 causes the roller 37 to move toward the narrower side of the cam chamber 36a, and the locking recess 34 protruding from the outer peripheral surface of the biasing ring 40.
It is locked to the top of a and the outer 3
6 generates a resistance force between the inner ring 34 and the inner ring 34.
a. As a result, the roller 37 causes the outer 36
And the inner 34 are engaged with each other, the rotation of the outer 36 is transmitted to the inner 34, the pinion gear 4 integral with the inner 34 rotates, and the pinion gear 4 meshes with the ring gear 33 to rotate the starting motor 2. The ring gear 3
Transmission to 3 starts the engine.

When the engine is started and the pinion gear 4 meshing with the ring gear 33 is rotated at high speed by the rotational force of the engine through the ring gear 33, the inner 34
Is faster than the rotation of the outer 36, the roller 37 moves toward the wider side of the cam chamber 36a against the biasing force of the spring 38 due to the relative rotation difference between the outer 36 and the inner 34. Thereby, the roller 37 and the outer 36
And the engagement with the inner 34 is released, the inner 3
The rotation of No. 4 is not transmitted to the outer 36, and overrun of the armature 11 can be prevented. In addition, the roller 37
Moves toward the wider side of the cam chamber 36a, the biasing ring 40 that has been pushed to the inner peripheral side of the groove 34b until then is restored by its own elastic force, so that the locking recess 34a of the inner 34 is The top part is slightly projected from the outer peripheral surface of the biasing ring 40 and is almost covered by the biasing ring 40. As a result, the roller 37, which has moved to the wider side of the cam chamber 36a, hardly collides with the locking recess 34a, and the behavior in the cam chamber 36a is stabilized.

After the engine is started, the starter switch OF is turned off.
The operation of the magnet switch 6 is stopped by F operation,
When the plunger, which had been sucked until then, returns to the initial position, the motor contact in the magnet switch 6 opens,
When the power supply to the starting motor 2 is stopped, the rotation of the armature 11 is stopped. Further, since the lever 44 engaged with the joint 45 swings to the side opposite to that at the time of engine start due to the return of the plunger, a retracting force acts on the spline tube 43 through the lever 44,
The pinion gear 4 disengages from the ring gear 33, retracts on the output shaft 3 together with the one-way clutch 5, and returns to the stationary position.

(Effect of this embodiment) In this embodiment, the biasing ring 40 is housed in the groove 34b of the inner 34 so that the outer peripheral surface is located between the deepest portion B and the top portion C of the locking recess 34a. Therefore, it is possible to reduce the resistance of the roller 37 and the locking recess 34a from colliding or being caught when the outer 36 and the inner 34 run idle. This improves the idling performance and stabilizes the behavior of the roller 37,
It is possible to prevent deformation due to the collision between the roller 37 and the locking recess 34a, and it is possible to prevent repeated fatigue of the spring 38 that biases the roller 37 in the cam chamber 36a. Also,
When the inner ring 34 and the outer layer 36 overrun, the urging ring 40 urges the roller 37 by its own elastic force to separate the roller 37 from the locking recess 34a.
The contact resistance with and the friction noise at the time of overrun are reduced, and the noise of the starter 1 can be reduced.

Since the urging ring 40 is in contact with the roller 37 at both ends in the longitudinal direction of the roller 37, the roller 37
It is possible to obtain a stable behavior by preventing the inclination of.
Further, the outer peripheral surface of the urging ring 40 is the side wall portion 3 of the outer 36.
Since it is restricted by the inner peripheral surface of 6b and the inner peripheral surface of the plate 39, it is possible to limit the centrifugal deformation of the urging ring 40 at the time of overrun to the range where the function of the clutch can be secured. In addition, the urging ring 40 is attached to the outer 36 and the plate 39.
Since the rollers 37 are centered on each other, the rollers 37 can be held in the respective cam chambers 36a of the outer 36 at equal positions, and the outer 36 and the inner 34 can be coaxial with each other during overrun. Further, since the outer peripheral surface of the urging ring 40 is restricted by the outer 36 and the plate 39, the inner 34 rotated at a high speed by the engine during overrun.
Compared to the side, since the outer 36 side rotates without load of the starter, the influence of centrifugal force is reduced and abnormal deformation of the urging ring 40 can be prevented.

(Second Embodiment) FIG. 5 is a sectional view of the one-way clutch 5 taken along the axial direction. The present embodiment is an example of a case in which the biasing ring 40 is press-fitted and fixed to the inner 34 so as to rotate integrally with the inner 34. As shown in FIG. 5, the urging ring 40 has a predetermined width in the longitudinal direction of the roller 37 (horizontal direction in FIG. 5), and about half of the width direction of the urging ring 40 protrudes outward from the end surface of the roller 37. One end of the biasing ring 40, which is inside the end surface of the roller 37, is elastically deformable in the groove 34b provided in the inner 34 in the radial direction, and the inner diameter side of the portion protruding from the end surface of the roller 37 is provided. It is press-fitted and fixed to the outer peripheral surface of the inner 34. Further, as shown in FIG. 6, the urging ring 40 has an outer peripheral surface in the radial direction at the top C of the locking recess 34a.
The size is set to be located on the outer peripheral side.

In the biasing ring 40 of this embodiment, one end side is elastically deformed at the time of torque transmission, and the roller 37 is locked with the recess 34a.
However, since the ring-shaped ring body has the other end press-fitted and fixed to the inner 34, it is always fixed and centered on the inner 34 even if centrifugal force is applied. Therefore, a problem (behavior of the roller 37 becomes unstable) due to eccentricity, which is a conventional problem, does not occur. The urging ring 40 is made of thin steel material, and the load of the roller 37 pressing the urging ring 40 due to the wedge shape of the cam chamber 36a formed in the outer 36 is the outer 36, the inner 34, and the roller of the present invention. Since it is set much smaller than the load transmitting torque between 37,
Even if a lubricant with a low friction coefficient is used, the urging ring 4
0 is deformable, and the roller 37 can enter the locking recess 34a.

(Third Embodiment) FIG. 7 is a sectional view of the one-way clutch 5 taken along the axial direction. Similar to the second embodiment, the present embodiment shows another example in which the biasing ring 40 is press-fitted and fixed to the inner 34. As shown in FIG. 7, the urging ring 40 is an annular ring body having a U-shaped cross section, and the roller 37 is in sliding contact with the outer peripheral surface of the urging ring 40, and the inner peripheral surface thereof is press-fitted and fixed to the inner 34. In the case of the present embodiment as well, as in the second embodiment, since the biasing ring 40 is always fixed to the inner member 34 and centered, no problems due to eccentricity or the like occur. Further, the same effect can be obtained even if the biasing ring 40 has a disc spring shape, the small diameter side is fixed to the inner 34, and the roller 37 is slidably contacted on the large diameter side.

(Modification) In the first embodiment, an example in which the pinion gear 4 is provided integrally with the inner 34 is shown, but it is shown in the second embodiment (see FIG. 5) and the third embodiment (see FIG. 7). As described above, the pinion gear 4 and the inner 34 are separately provided,
Both may be fixed to each other in the circumferential direction and the axial direction by a method such as press fitting or welding.

[Brief description of drawings]

FIG. 1 is a sectional view (a sectional view taken along line AA in FIG. 4) of a one-way clutch in an overrun state.

FIG. 2 is a sectional view of the one-way clutch during torque transmission (see FIG.
AA sectional view of FIG.

FIG. 3 is a half sectional view of a starter.

FIG. 4 is a sectional view taken along the axial direction of the one-way clutch.

FIG. 5 is a sectional view taken along the axial direction of the one-way clutch (second embodiment).

FIG. 6 is a sectional view of a one-way clutch in an overrun state (second embodiment).

FIG. 7 is a sectional view taken along the axial direction of the one-way clutch (third embodiment).

FIG. 8 is a sectional view of the one-way clutch proposed in the prior application.

[Explanation of symbols]

 1 Starter 2 Starter Motor 3 Output Shaft 4 Pinion Gear 5 One-way Clutch 34 Inner 34a Locking Recess 34b Annular Groove 36a Cam Chamber (Accommodating Chamber) 36 Outer 37 Roller 38 Spring (Biasing Member) 39 Plate 40 Biasing Ring (Annular Ring) Elastic body) B Deepest part C Topmost part

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Masanobu Masami, 1-1, Showa-cho, Kariya city, Aichi Prefecture Nihondenso Co., Ltd.

Claims (8)

[Claims] 1. An outer having a wedge-shaped accommodating chamber on an inner peripheral surface thereof, a roller accommodated in the accommodating chamber, and a lock disposed on an inner peripheral side of the outer and locking an outer peripheral surface of the roller. A one-way clutch comprising an inner having a recess and transmitting torque from the outer to the inner only in one direction via the roller, wherein the outer peripheral surface of the inner intersects with the locking recess to form a circle. Direction, and an annular groove formed deeper than the locking recess, and an annular body housed in the groove, which is elastically deformable in the radial direction and has an outer peripheral surface in the radial direction. An annular elastic body located between the deepest part and the top part of the stop recess is provided, and at the time of torque transmission from the outer to the inner, the roller bends the annular elastic body toward the inner peripheral side, The inner recess is locked in the locking recess. One-way clutch rotating During larger overrun the rotation of the outer, the roller characterized in that the disengaged from the locking recess while being urged toward the outer peripheral direction by the elastic force of the annular elastic body. 2. The one-way clutch according to claim 1, wherein the annular elastic body is in contact with the roller at both ends in the longitudinal direction of the roller. 3. The annular elastic body has a portion protruding outward from the end surface of the roller in the longitudinal direction of the roller, and the outer peripheral surface of the protruding portion is adapted to move the outer or the roller in the axial direction. 3. The one-way clutch according to claim 1, wherein the annular elastic body is regulated by a regulating plate to prevent the annular elastic body from being deformed toward the outer peripheral side. 4. An urging member for urging the roller in a narrow direction of the storage chamber, wherein the annular elastic body is set so as not to be deformed by the urging force of the urging member. The one-way clutch according to any one of items 1 to 3. 5. An outer having a wedge-shaped accommodating chamber on an inner peripheral surface thereof, a roller accommodated in the accommodating chamber, and a lock arranged on an inner peripheral side of the outer and locking the roller on an outer peripheral surface. A one-way clutch comprising an inner having a recess and transmitting torque from the outer to the inner only in one direction via the roller, the annular being formed deeper than the locking recess on the outer peripheral surface of the inner. , And one end of the groove is an annular body that is elastically deformable in the radial direction and the other end is fixed to the inner, and the one or the other end of the annular body has the outer periphery in the radial direction. A one-way clutch, which is an annular elastic body formed to have substantially the same diameter as the maximum diameter of the recess. 6. The one-way clutch according to claim 5, wherein the annular elastic body is in contact with the roller at both ends in the longitudinal direction of the roller. 7. An urging member for urging the roller in a narrow direction of the accommodating chamber, wherein the annular elastic body is deformed by the urging force of the urging member, but the outer diameter at one end is the locking. 7. The one-way clutch according to claim 5, wherein the diameter is set so as not to be less than the diameter of the top of the recess. 8. A starter for transmitting a rotational force of a starting motor to an output shaft to rotationally drive a pinion gear, wherein the one-way clutch according to claim 1 transmits power from the starting motor to the output shaft. A starter characterized by being interposed in the system.