KR101034104B1

KR101034104B1 - Dial recliner

Info

Publication number: KR101034104B1
Application number: KR1020080097930A
Authority: KR
Inventors: 백홍전; 채수민
Original assignee: 주식회사 오스템
Priority date: 2008-10-07
Filing date: 2008-10-07
Publication date: 2011-05-13
Also published as: WO2010041839A2; WO2010041839A3; KR20100038820A

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dial recliner, wherein an eccentric arc portion 133 and a clutch shoe 135 and 136 are formed on both sides of the cam 130 for rotating the sector gear 120 with respect to the holder 110. And a single clutch element having a pair of one-way clutch portions 151 and 152 inserted between the clutch shoes 135 and 136 and the bearing 140 on the side of the sector gear 120 provided outside thereof, for example. For example, characterized in that it comprises a C-type elastic member 150. As a result, a simple structure, a reduction in the number of parts, and a simplification of the manufacturing process can be achieved, and play between parts can be minimized.

Dial recliner, prevents play and reduces parts

Description

Dial Recliner {DIAL RECLINER}

The present invention relates to a recliner mounted on a vehicle seat and capable of reclining a seatback, and in particular, a dial recliner provided to adjust a rotation angle of the seatback according to a rotation amount of a knob connected to the recliner. It is about.

The dial recliner is basically provided with a holder and a sector gear in which different teeth and inner teeth are formed, respectively, while the sector gear is rotated in the holder in the state of tooth engagement with the holder-side internal gear (idle). It is usually common in terms of the principle that the seatback fastened integrally therewith by performing self rotation (rotation) can be rotated back and forth.

However, the conventional dial recliner has a disadvantage in that the manufacturing process is complicated as the structure is complicated and the number of parts is required.

In addition, it has been pointed out that the conventional dial recliner is difficult to manufacture and the manufacturing cost is also increased due to the high processing precision in terms of fastening and interaction between parts.

In addition, according to the conventional dial recliner, there is a problem in that the seatback adjusted by rotation is gradually turned back while being fixed by a repeated press or impact by the seated person during use.

In addition, the phenomenon in which the seatback is leaned back was mainly caused by the clearance between the parts constituting the dial recliner, in particular, the radial clearance around the drive shaft for adjusting the dial recliner.

The object of the present invention is to simplify the manufacturing process by reducing the number of parts and the structure is simple compared to the prior art, and to minimize the occurrence of play between parts even without increasing the processing precision of the components by the seat back during external impact It is to provide a dial recliner that can be prevented from rolling over.

In order to achieve the above object, the present invention provides a dial recliner, comprising: a holder having an inner tooth portion formed on an outer circumferential surface thereof and a boss formed on a center thereof; A sector gear formed on an outer circumferential surface thereof with an outer tooth portion engaged with the inner tooth portion of the holder, the circular receiving portion being eccentrically coupled to the holder and having a circular receiving portion eccentrically from the center of the holder; A bearing which is inserted into an accommodation portion of the sector gear and is supported radially by the sector gear, and is accommodated in a state in which the boss is eccentrically spaced apart; A central shaft portion inserted into the boss, an eccentric arc portion whose inner circumferential surface is slide-rotated along the outer circumferential surface of the boss, and protruded on both sides of the eccentric arc portion to form wedge grooves symmetrically with each other in the circumferential direction between the bearing and the bearing. A cam formed with a pair of clutch shoes; And a single clutch element having a pair of one-way clutch portions inserted into each of the wedge grooves, the pair of unidirectional clutch portions for preventing friction of rotation of the sector gear by generating frictional forces in opposite circumferential directions, respectively, in contact with the corresponding clutch shoe and the inner circumferential surface of the bearing. It provides a dial recliner characterized in that.

Here, the clutch element is a C-type elastic member accommodated between the bearing and the boss, but received in the space opposite the eccentric arc portion, one end of the C-shaped elastic member is inserted into one side wedge groove and the other end is wedge The pair of one-way clutch portions may be formed by being inserted into the groove portion.

At this time, the C-type elastic member is accommodated between the bearing and the boss with both ends in the tangential direction, thereby receiving elastic restoring force in the direction in which the one end and the other end are inserted into the corresponding wedge grooves, whereby It is also possible to prevent the occurrence of radial play between the cam on the inner side, the bearing on the outer side, and the cam and the boss between the cam and the boss.

In addition, the pair of clutch shoes may each slide so that the inner circumferential surface is in surface contact with the outer circumferential surface of the boss.

On the other hand, the present invention is a dial recliner (dial recliner), the inner tooth is formed on the outer peripheral surface and the boss (boss) is formed in the center; A sector gear formed at an outer circumferential surface thereof with an outer tooth portion engaged with the inner tooth portion of the holder, the circular receiving portion being eccentrically coupled with the holder and having a center of eccentricity with the center of the holder; A bearing which is inserted into an accommodation portion of the sector gear and is supported radially by the sector gear, and is accommodated in a state in which the boss is eccentrically spaced apart; A central shaft portion inserted into the boss, an eccentric arc portion in which the inner circumferential surface slides along the outer circumferential surface of the boss, and protruded on both sides of the eccentric arc portion, the wedge groove portion symmetrically with each other in the circumferential direction between the boss A cam having a pair of clutch shoes formed thereon; And inserted into each of the wedge grooves so as to contact the outer circumferential surfaces of the clutch shoe and the boss to generate frictional forces in opposite circumferential directions and press the cam in a radial direction to prevent rotation of the sector gear through the cam. A dial recliner is provided comprising a single clutch element in which a pair of one-way clutch portions are formed.

Here, the clutch element is a C-type elastic member accommodated between the bearing and the boss, but received in the space opposite the eccentric arc portion, one end of the C-shaped elastic member is inserted into one side wedge groove and the other end is wedge The pair of clutch portions may be formed by being inserted into the groove portion.

At this time, the C-type elastic member is accommodated between the bearing and the boss with both ends in the tangential direction, thereby receiving elastic restoring force in the direction in which the one end and the other end are inserted into the corresponding wedge grooves, whereby A pressing force may be exerted to prevent radial play between the inner bosses, the outer cams, and the cams and the bearings.

In addition, the pair of clutch shoes may each slide so that the outer circumferential surface is in surface contact with the inner circumferential surface of the bearing.

According to the present invention as described above, the structure is simple compared to the prior art and can simplify the manufacturing process by reducing the number of parts, even without increasing the machining precision of the component parts, the dial reckle can minimize the occurrence of play between parts You can get a liner.

In particular, the pair of clutch portions inserted into the wedge groove portions formed between the inner cam and the outer bearing can be formed by a single clutch element, thereby reducing the number of parts and simplifying the manufacturing process.

In addition, the clearance that can occur in the radial direction between the parts around the drive shaft leads to the size of the formation space of the wedge groove portion, the size of the wedge groove portion so as to fill the long and short end of the depth to which the clutch portion is inserted as described above As a result, the occurrence of radial play between components can be prevented.

At this time, when the single clutch element is inserted in a somewhat open state as the C-type elastic member, elastic restoring force is exerted to be inserted into the wedge groove as both ends of the clutch portion, whereby both ends of the C-type elastic member are exerted. Since it is always inserted into the wedge groove as much as possible, as a result, the occurrence of radial play between components can be prevented.

Dial recliner 100 according to the first embodiment of the present invention, as shown in Figure 1, the holder 110 and the sector gear 120, and the cam 130, bearing and supported between them, bearing 140, a C-type elastic member 150, and a housing 160 for maintaining the coupling between the holder 110 and the sector gear 120.

An inner tooth 111 is formed in a ring shape on the outer circumferential surface of the holder 110, and a boss 112 for supporting the shaft is formed at the center of the holder 110.

The sector gear 120 has an outer tooth portion 121 formed on the outer circumferential surface thereof and is tooth-coupled with the inner tooth 111 of the holder 110 through this.

At this time, the pitch circle of the outer tooth portion 121 has a smaller radius than the inner tooth portion 111, and thus the number of teeth formed on the outer tooth portion 121 is the number of teeth formed on the inner tooth portion 111. One less than the number.

Therefore, when the holder 110 and the sector gear 120 are coupled, the boss 112 of the holder 110 and the shaft hole 122 of the sector gear 120 are eccentric with each other.

A circular accommodating part 123 having a predetermined radius is formed around the shaft hole 122.

The cam 130 has a central shaft portion 131 (FIG. 3) and an eccentric shaft portion 132 which are eccentric with each other in the axial direction. The central shaft portion 131 is inserted into the boss 112 of the holder 100, and the eccentric shaft portion 132 is inserted into the shaft hole 121 of the sector gear 120.

In addition, the cam 130 has an eccentric arc portion (133 of FIG. 6) spaced apart at one portion in the radial direction of the central axis portion 131.

A through hole 134 having a rectangular cross section is formed around the central axis 131 of the cam 130 in the axial direction. The shaft of the rotary knob is inserted into the through hole 134 to achieve rotation control of the dial recliner 100.

One side of the bearing 140 is fitted to the receiving portion 123 of the sector gear 120 and is radially supported by the sector gear 120.

The boss 112 of the holder 110 is accommodated in an eccentrically spaced state inside the bearing 140. The eccentric arc portion (133 of FIG. 6) and the C-type elastic member 150 to be described later are inserted into the spaced space.

C-type elastic member 150 is a clutching element (clutching element) for performing the locking and unlocking between the cam 130 and the bearing 140, the one-way clutch that generates the friction force in the circumferential direction opposite their respective ends Part 151, 152.

As shown in FIG. 3, the housing 160 supports the right side surface of the sector gear 120 on one side extending inwardly and the left outer peripheral surface of the holder 110 on the other side.

FIG. 2 is a front view illustrating a coupling state of the dial recliner 100 of FIG. 1. The center of the housing 160, that is, the center of the holder 110 is C1, and the center of the sector gear 120 is C2. As a result, it is formed at a position eccentrically away from the C1.

3 is a side cross-sectional view of the dial recliner 100 cut along the line AA of FIG. 2. As shown in the drawing, the holder 110 and the sector gear 120 are in the state where the lower ends are tooth-coupled with each other, so that the center axis C2 of the sector gear 120 is the center axis C1 of the holder 110. Located at the bottom

The bearing 140 has a right end inserted into the receiving portion 123 of the sector gear 120 to be radially supported by the sector gear 120, and the center of the bearing 140 is also the center C2 of the sector gear 120. Matches.

At this time, the inner circumferential surface of the eccentric arc portion 133 of the cam 130 is formed along the outer circumferential surface of the boss 112 of the holder 110. That is, the inner circumferential surface of the eccentric arc portion 133 forms an arc centered on the center C1 of the boss 112.

The outer circumferential surface of the eccentric arc portion 133 maintains a state accommodated inside the inner circumferential surface of the bearing 140.

Therefore, the center C2 of the sector gear 120 is always located in the direction in which the eccentric arc portion 133 is located from the center C1 of the boss 112, and the holder 110 and the sector in that direction. Tooth coupling of the gear 120 is made. That is, in FIG. 3, since the eccentric arc part 133 is located vertically downward from the center C1 of the holder 110, the center C2 of the sector gear 120 is also vertically lower than the center C1 of the holder 110. The tooth coupling between the holder 110 and the sector gear 120 is also made in the direction of the center C2 with respect to the center C1, ie in each vertical lower end of the holder 110 and the sector gear 120. do.

The relative position of the center C2 with respect to C1 and the tooth engagement position between the holder 110 and the sector gear 120 are made in a direction coinciding with the position of the eccentric arc portion 133 according to the rotation of the cam 130. do.

4 is a front sectional view of the dial recliner 100 cut along the line BB of FIG. 3.

As described above, the inner tooth portion 111 of the holder 110 and the outer tooth portion 121 of the sector gear 120 are in a state where the lower ends are tooth-coupled with each other, which is the eccentric arc portion 133 of the cam 130. The rotational position of is due to the vertical downward position.

The cam 130 is rotated and supported by the central shaft portion 131 in contact with the boss 112 of the holder 110, the eccentric arc portion 133 formed integrally with the central shaft portion 131 is the central shaft portion 131 As they rotate, they rotate together.

The eccentric arc portion 133 slides in an interview state along the outer circumferential surface of the boss 112 as the inner circumferential surface forms an arc around the center C1 of the holder 110.

The outer circumferential surface of the eccentric arc portion 133 is placed inside the inner circumferential surface of the bearing 140.

As the cam 130 rotates, the eccentric center C2, that is, the center of the sector gear 120, is positioned at the same angle as the rotated angle of the eccentric arc part 133. That is, the center C2 of the sector gear 120 has a trajectory of a circle having a radius of a distance spaced from the center C1 of the holder 110 according to the rotation of the eccentric arc part 133. .

The outer tooth 121 of the sector gear 120 revolves on the inner tooth 111 of the holder 110 as the cam 130 rotates, and at the same time the sector gear 120 is relatively idle. It rotates in the opposite direction.

According to the rotation of the sector gear 120, a seatback (not shown) coupled integrally therewith is rotated.

FIG. 5 shows a state in which the cam 130 is rotated 45 ° counterclockwise from the state of FIG. 4. As shown, as the eccentric arc portion 133 on the cam 130 side rotates 45 °, the sector gear 120 also rotates along the inner tooth 111 of the holder 110, and its center C2 also It can be seen that it rotates 45 ° about the center C1 of the holder 110.

On the other hand, on both sides of the eccentric arc portion 133 of the cam 130, a pair of clutch shoes (135) (135 and 136) protrudingly formed to face each other in the circumferential direction.

Each of the clutch shoes 135 and 136 is formed such that an inner circumferential surface forms an arc around the center C1 of the holder 110 to interview the outer circumferential surface of the boss 112.

The outer circumferential surfaces of the clutch shoes 135 and 136 form a pair of wedge groove portions W1 and W2 extending in the circumferential direction between the inner circumferential surfaces of the bearing 140.

The pair of wedge groove portions W1 and W2 are formed in directions facing each other.

On the other hand, the C-shaped elastic member 150 is accommodated in the space opposite to the eccentric arc portion 133 on the cam 130 side among the space formed between the inner boss portion 112 and the outer bearing 140. .

At this time, as shown in Figure 4, the left end portion 151 of the C-shaped elastic member 150 is inserted into the wedge groove portion (W1) of the left side of the pair of wedge groove portions (W, W2), One end 152 is inserted into the wedge groove portion W2 on the right side.

According to the C-type elastic member 150, the two-way rotation of the sector gear 120 is prevented.

That is, the left end portion 151 of the C-type elastic member 150 allows the bearing 140 to rotate in the clockwise direction, but generates a frictional force to prevent the bearing 140 from rotating in the counterclockwise direction. do. Similarly, the right end portion 152 of the C-shaped elastic member 150 allows the bearing 140 to rotate counterclockwise but rotates clockwise to perform a one-way clutch function that prevents friction through generation. .

Therefore, both ends 151 and 152 of the C-shaped elastic member 150, as long as it prevents the sector gear 120 into which the bearing 140 is inserted from being impacted from the outside, thereby rotating in opposite directions. It functions as a pair of one-way clutch portions 130.

In particular, the clutch element for performing the function of the pair of one-way clutch portion 130 is achieved by a single C-type elastic member 150 as described above can obtain the effect of component reduction.

In addition, the C-type elastic member 150, even if there are some errors in terms of thickness, length, etc., the depth inserted into the wedge grooves (W1, W2) is adjusted only to achieve the function as the clutch element The problem does not occur.

Similarly, the machining of the boss 112 of the holder 110, the central shaft portion 131 of the cam 130, the eccentric arc portion 133, the clutch shoes 135, 136, the bearing 140, and the like is somewhat processed. Even if there are phase errors, these errors can all be concentrated on the change in thickness or length of the wedge grooves W1 and W2.

That is, the space shape of the wedge groove portions W1 and W2 may be deformed due to the existence of all the above errors, and the insertion depths of the both ends 151 and 152 of the C-shaped elastic member 150 inserted therein may vary. However, the function as the clutch element is normally maintained.

In particular, the C-type elastic member 150 contacts and presses a pair of clutch shoes 135 and 136 inward through the both ends 151 and 152 inserted into the wedge groove portions W1 and W2 in the center direction. The contact between the boss 112 and the outer side is always in contact with the bearing 140, so that the play between the boss 112, the cam 130, the C-type elastic member 150, the bearing 140 as a whole Do not occur.

This is achieved by being accommodated between the bearing 140 and the boss 112 in a state in which both ends 151 and 152 of the C-type elastic member 150 are opened in a tangential direction.

At this time, the both ends (151, 152) by the elastic restoring force of the C-type elastic member 150 is continuously entered in the direction to be inserted into the corresponding wedge groove (W1, W2), C-type elastic member 150 ) And the cam 130 at its inner side, the C-shaped elastic member 150 and the bearing 140 at its outer side, and the cam 130 and the boss 112 at its inner side. This will not happen.

Accordingly, even when the dial recliner 100 is impacted from the outside, the bearing force is easily transmitted and easily transferred due to the contact between the boss 112, the cam 130, the C-type elastic member 150, and the bearing 140. By being dispersed, the sector gear 120 may be prevented from being rotated in the holder 110 due to the external impact.

On the other hand, when the cam 130 itself is driven to rotate, the rotation of the cam 130 is achieved by the following principle.

That is, when the cam 130 is rotated in the counterclockwise direction by rotating a knob (not shown) coupled to the through hole 134, in FIG. 4, the eccentric arc part 133 is integrally counterclockwise. By rotating to rotate the sector gear 120 counterclockwise through the bearing 140 having an eccentric center (C2). Of course, in this case, the eccentric center C2 also moves counterclockwise about the center C1 of the holder 110.

At this time, in the wedge groove portion W1 on the left side, since the radial length at one point in the space becomes larger (see FIG. 5), the counterclockwise rotation of the eccentric arc portion 133 is C-type elastic. It is not hindered by the left end portion 151 of the member 150.

On the other hand, in the wedge groove portion W2 on the right side, the right end portion 152 of the C-shaped elastic member 150 is pressed in contact with the clutch shoe 136 and is pushed in the counterclockwise direction to rotate.

As the C-shaped elastic member 150 is pushed and rotated counterclockwise by the right clutch shoe 136, the left end portion 151 is pushed into the newly formed wedge groove portion W1 to form an interlocking relationship.

As described above, the rotation of the sector gear 120 may be achieved through the counterclockwise rotational drive of the cam 130, which is the same principle in the clockwise rotational drive of the cam 130. Will be omitted.

7 is a cross-sectional view of the engaged state of the dial recliner 100 according to the second embodiment of the present invention.

As shown, the pair of clutch shoes 235, 236 (see FIG. 8) formed in the cam 230 has an outer circumferential surface in surface contact with the inner circumferential surface of the bearing 240 and each inner circumferential surface with the boss 212. Wedge grooves W3 and W4 are formed.

Both end portions 251 and 252 of the C-shaped elastic member 250 are inserted into the respective wedge grooves W3 and W4 so that the outside thereof contacts the bosses 212 and the inside of the clutch shoes 235 and 236, respectively.

At this time, both ends (251, 252) of the C-shaped elastic member 250 serves to inhibit the rotation of the sector gear 220 by the external force by pressing the cam 230 in the radial direction.

In addition, the C-type elastic member 250, even if there is some error in terms of its thickness, length, etc., the depth to be inserted into the wedge grooves (W2, W3) is adjusted only to achieve the function as the clutch element The problem does not occur.

Similarly, the machining of the bosses 212 of the holder 210 and the center shaft portion 231 of the cam 230, the eccentric arc portion 233, the clutch shoes 235, 236, the bearing 240, and the like is somewhat performed. Even if an error exists in the image, all of these errors can be focused on the change in thickness or length of the wedge groove portions W3 and W4.

That is, the space shape of the wedge groove portions W3 and W4 may be deformed due to the existence of all the above errors, and the insertion depths of both ends 251 and 252 of the C-shaped elastic member 250 inserted therein may vary. However, the function as the clutch element is normally maintained.

In particular, the C-type elastic member 250 is radially contacted and pressed in a pair of clutch shoes 235, 236 to the outside through both ends (251, 252) inserted into the wedge grooves (W3, W4). By maintaining the state, and always in contact with the boss 212 on the inside so as to prevent the play between the boss 212, the C-shaped elastic member 250, the cam 230, the bearing 240 as a whole. .

This is achieved by being accommodated between the bearing 240 and the boss 212 in a state in which both ends 251 and 252 of the C-shaped elastic member 250 are opened in a tangential direction.

At this time, the both ends (251, 252) by the elastic restoring force of the C-type elastic member 250 is continuously entered in the direction to be inserted into the corresponding wedge grooves (W3, W4), C-type elastic member 250 Gap between the C-shaped elastic member 250 and its outer cam 230, and between the cam 230 and its bearing 240, It does not occur.

Accordingly, even when the dial recliner 200 is impacted from the outside, the bearing force is easily transmitted and easily transferred due to the contact between the boss 212, the C-type elastic member 250, the cam 230, and the bearing 240. By being distributed, the sector gear 220 may be prevented from being rotated in the holder 210 due to the external impact.

On the other hand, the rotational drive of the cam 230, when the counter-clockwise rotation of the cam 230, the wedge groove portion W3 of the left side becomes wider so that the left clutch shoe 235 is a C-type elastic member It is separated from the left end 251 of the 250 and its rotation is not hindered, and the C-shaped elastic member 250 end 252 on the side of the wedge groove portion W4 on the right side is pushed together by the right clutch shoe 236 to be held together. It will rotate clockwise.

Since the cam 230 is driven in the clockwise direction, the description thereof will be omitted.

In addition, since the features of the dial recliner 200 according to the present embodiment are similar to those of the dial recliner 100 according to the first embodiment, a description thereof will be omitted herein.

On the other hand, the dial recliner (100, 200) and its modifications described above are only embodiments for explaining the present invention, but the scope of the present invention is not limited to these, the scope of the present invention The scope of the rights to the technical scope is defined by the claims to be described later and their equivalents.

1 is an exploded perspective view showing a dial recliner according to a first embodiment of the present invention;

FIG. 2 is a front view showing the engaged state of the dial recliner of FIG. 1; FIG.

3 is a side cross-sectional view taken along line AA of FIG. 2;

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

5 is a front sectional view showing a state after the cam is driven a predetermined angle in the dial recliner of FIG.

6 is an enlarged perspective view of the cam as one component of the dial recliner of FIG.

7 is a front sectional view showing the engagement state of the dial recliner according to the second embodiment of the present invention;

FIG. 8 is an enlarged perspective view illustrating a cam as one component of the dial recliner of FIG. 7.

100: dial recliner 110: holder

111: internal tooth 112: boss

120: sector gear 121: outer teeth

122: shaft ball 123: receiving portion

130: cam 131: central axis

132: eccentric shaft 133: eccentric arc

134: through hole 135, 136: clutch shoe

140: bearing 150: C type elastic member

151 and 152: one-way clutch 160: housing

Claims

In dial recliner,

A holder having an inner tooth portion formed on an outer circumferential surface thereof and having a boss formed in the center thereof;

A sector gear formed on an outer circumferential surface thereof with an outer tooth portion engaged with the inner tooth portion of the holder, the circular receiving portion being eccentrically coupled to the holder and having a circular receiving portion eccentrically from the center of the holder;

A bearing which is inserted into an accommodation portion of the sector gear and is supported radially by the sector gear, and is accommodated in a state in which the boss is eccentrically spaced apart;

A central shaft portion inserted into the boss, an eccentric arc portion whose inner circumferential surface is slide-rotated along the outer circumferential surface of the boss, and protruded on both sides of the eccentric arc portion to form wedge grooves symmetrically with each other in the circumferential direction between the bearing and the bearing. A cam formed with a pair of clutch shoes; And

A single clutch element formed in each of the wedge grooves and having a pair of one-way clutch portions formed in contact with a corresponding clutch shoe and an inner circumferential surface of the bearing to generate frictional forces in opposite circumferential directions to prevent rotation of the sector gear; ,

The clutch element is a C-type elastic member accommodated between the bearing and the boss but accommodated in an opposite space of the eccentric arc, wherein one end of the C-shaped elastic member is inserted into one wedge groove and the other end is connected to the other wedge groove. Dial recliner characterized in that the pair of one-way clutch portion by being inserted.

delete

The method of claim 1,

The C-shaped elastic member is accommodated between the bearing and the boss with both ends tangentially opened, whereby the one end portion and the other end portion receive elastic restoring force in the direction in which the respective wedge grooves are inserted, thereby reducing the radial force. A dial recliner which is exerted to prevent radial play between the inner cam, the outer bearing, and the cam and the boss.

The method of claim 1,

And the pair of clutch shoes are rotated in a state in which the inner circumferential surface thereof is in surface contact with the outer circumferential surface of the boss.

In dial recliner,

A sector gear formed at an outer circumferential surface thereof with an outer tooth portion engaged with the inner tooth portion of the holder, the circular receiving portion being eccentrically coupled with the holder and having a center of eccentricity with the center of the holder;

A central shaft portion inserted into the boss, an eccentric arc portion whose inner circumferential surface is slide-rotated along the outer circumferential surface of the boss, and protruded on both sides of the eccentric arc portion to form a wedge groove portion symmetrically with each other in the circumferential direction between the boss A cam formed with a pair of clutch shoes; And

A pair inserted into each of the wedge grooves to contact the outer circumferential surfaces of the clutch shoe and the boss to generate frictional forces in opposite circumferential directions and press the cam in a radial direction to prevent rotation of the sector gear through the cam; A single clutch element formed with a one-way clutch portion of

The clutch element is a C-type elastic member accommodated between the bearing and the boss but accommodated in an opposite space of the eccentric arc, wherein one end of the C-shaped elastic member is inserted into one wedge groove and the other end is connected to the other wedge groove. A dial recliner comprising the pair of clutch portions by being inserted.

delete

The method of claim 5,

The C-shaped elastic member is accommodated between the bearing and the boss with both ends tangentially opened, whereby the one end portion and the other end portion receive elastic restoring force in the direction in which the respective wedge grooves are inserted. A dial recliner which is exerted to prevent radial play between the inner boss and the outer cam and between the cam and the bearing.

The method of claim 5,

And the pair of clutch shoes are each rotated while the outer circumferential surface is in surface contact with the inner circumferential surface of the bearing.