KR101072791B1 - dial recliner - Google Patents

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 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. And the elastic pressing means 160 for urging the C-type elastic member 150 in the radial direction. 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. In addition, due to the machining error between parts during the rotation operation of the dial recliner can be reduced to some extent the deviation of the rotation operation force according to the rotation section.

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 component parts when mounted on the seat An object of the present invention is to provide a dial recliner that can prevent the seat back from being flipped due to an impact.

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 at an outer circumferential surface thereof with an outer tooth portion engaged with the inner tooth portion of the holder to perform a rolling motion in the holder and have a circular receiving portion having a center eccentric from the center of the holder; A bearing which is inserted into a receiving portion of the sector gear and is supported in a radial direction, and is accommodated in a state in which the boss is eccentrically spaced inside; A central shaft portion inserted into the boss, an eccentric cam portion rotatably coupled to the inner circumferential surface of the bearing, and a pair of clutch shoes forming a wedge groove portion symmetrically with each other in the circumferential direction between the bearing A cam formed of; A C-shaped elastic member accommodated between the bearing and the boss to form a pair of one-way clutch portions by having one end inserted into one wedge groove and the other end inserted into the other wedge groove; And an elastic pressing means accommodated between the C-type elastic member and the boss to pressurize the C-type elastic member in a radial direction.

Here, the elastic pressing means may be a U-shaped spring.

According to the present invention as described above, compared to the prior art, the structure is simple, and the number of parts can be simplified to simplify the manufacturing process, and even without increasing the processing precision of the component parts, the dial recliner can minimize the occurrence of play between parts. Can be obtained.

In particular, a 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 C-shaped elastic member, 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 of the depth that is inserted both ends of the C-type elastic member as described above By making it possible to fill in short and short, the occurrence of radial play between parts can be prevented as a result.

Here, the C-type elastic member is inserted between the bearing and the boss in a somewhat open state, thereby exerting elastic restoring force to be inserted into the wedge groove as both ends of the clutch portion, whereby both ends of the C-type elastic member are always Since the state is inserted into the wedge groove to the maximum, as a result, the occurrence of radial play between parts can be prevented.

In particular, according to the present invention by pressing the C-type elastic member in the radial direction through the elastic pressing means, for example, U-shaped spring to be inserted into the wedge groove in the state where the C-shaped elastic member is somewhat open to perform a function When rotating the dial recliner, it is possible to prevent the variation of the operating force according to the section in which the knob rotates due to the radial machining error between the parts, thereby providing a uniform operating force over all the sections in which the knob rotates. Can be.

1 and 2 is an exploded perspective view showing a dial recliner according to an embodiment of the present invention,
3 is a front view illustrating a coupling state of the dial recliner of FIG. 1;
4 is a side cross-sectional view taken along line AA of FIG. 3;
5 is a front sectional view taken along line BB of FIG. 4;
6 is a front sectional view showing a state in which the cam is rotated a predetermined angle in the dial recliner of FIG. 5;
7 is a front view of a cam that is one component of the dial recliner of FIG. 1.

Dial recliner 100 according to an embodiment of the present invention, as shown in Figures 1 and 2, the holder 110 and the sector gear 120, and the cam 130 is received and supported therebetween, It includes a bearing 140, a C-shaped elastic member 150, a U-shaped spring 160, and includes a housing 170 for maintaining the coupling between the holder 110 and the sector gear 120.

An inner tooth 111 is formed in a ring shape at the outer circumferential portion 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 an outer circumferential surface thereof and is tooth-coupled with the inner tooth portion 111 of the holder 110 through the outer tooth portion 121.

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.

Around the shaft hole 122, a receiving portion 123 having a substantially constant radius is formed to protrude in an axial direction.

As shown in FIGS. 1, 2, and 7, the cam 130 is provided with a central shaft portion 131 and an eccentric shaft portion 132 which are eccentric with each other on both sides in the axial direction. The eccentric cam portion 137 is formed integrally with these.

The eccentric cam portion 132 forms an eccentricity with the central shaft portion 131 and is concentric with the eccentric shaft portion 132.

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 spaced apart from one portion in the radial direction of the central axis portion 131.

The cam 130 penetrates the central shaft portion 131 and the eccentric shaft portion 132 in common and has a cross-sectional through hole 134 formed in the axial direction. The shaft of the rotary knob (not shown) is inserted into the through hole 134 to achieve rotation control of the dial recliner 100.

The bearing 140 having a circular ring shape has one side (the right side in FIG. 1) fitted to the receiving portion 123 of the sector gear 120 and is supported radially by the sector gear 120.

The boss 112 of the holder 110 is accommodated in an eccentrically spaced radially spaced interior of the bearing 140. In the spaced space, the eccentric arc portion 133 of the cam 130 and the C-type elastic member 150 and the U-shaped spring 160 to be described later are inserted.

C-type elastic member 150 is a clutch element for locking and unlocking the relative rotation between the cam 130 and the bearing 140, the one end of the friction force in the circumferential direction opposite to each other One-way clutch parts 151 and 152 are formed.

As shown in FIG. 4, the housing 170 rotatably supports the sector gear 120 to one side (right side in FIG. 4) extending inwardly, and to the other side (left side in FIG. 4). Is rotatably supported while surrounding the left outer periphery of the holder 110.

FIG. 3 is a front view showing the engagement state of the dial recliner 100 of FIG. 1, wherein the center of the housing 170, that is, the center of the holder 110 (C in FIG. 4) is C1, and the sector gear 120 is closed. The center is C2, and is formed at a position eccentrically downward in comparison with C1.

4 is a side cross-sectional view of the dial recliner 100 cut along the line AA of FIG. 3.

As shown, the center axis C2 of the sector gear 120 is located below the center axis C1 of the holder 110, which means that the holder 110 and the sector gear 120 each have their lower ends. Means that the teeth are bonded to each other.

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.

The inner circumferential surface of the eccentric arc portion 133 of the cam 130 coincides with the outer circumferential surface of the boss 112 of the holder 110, and the outer circumferential surface of the eccentric arc portion 133 is maintained inside the inner circumferential surface of the bearing 140. do.

The eccentric shaft portion 132 of the cam 130 is eccentric with the central shaft portion 131 and is inserted into the shaft hole 122 of the sector gear 120.

Meanwhile, as shown in FIGS. 1 and 2, the eccentric cam portion 137 of the cam 130 is concentric with the eccentric shaft portion 132 and is inserted into the inner circumferential surface of the bearing 140.

Therefore, when the cam 130 rotates about the axis C1 of the central shaft portion 131, the eccentric cam portion 137 has a constant amount of eccentricity C1C2 about the axis C1, similarly to the eccentric shaft portion 132. The bearing 140 is coupled to the eccentric cam portion 137 so as to be rotatably concentrically rotatable therein so as to make a rolling motion with the holder 120 while being in sliding contact with the eccentric cam portion 137. do.

In other words, the sector gear 120 accommodated so that the bearing 140 coincides with the receiving portion 123 pivots about C1 with the eccentricity C1C2 together with the bearing 140, and at the same time, The outer tooth 121 is clouded on the inner tooth 111 of the holder 110.

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

The center C2 of the sector gear 120 is positioned from the center C1 of the boss 112 in the direction in which the outer tooth 121 is tooth-connected with the inner tooth 111 of the holder 110. 5 in the downward direction, and in FIG. 6, the right 45 degree direction.

Here, the relative position of the center C2 with respect to C1 and the tooth coupling between the holder 110 and the sector gear 120 are made on the eccentric direction of the eccentric cam portion 137 according to the rotation of the cam 130.

In FIG. 5, the lower teeth of the inner tooth 111 of the holder 110 and the outer tooth 121 of the sector gear 120 are tooth-coupled with each other.

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.

In the present embodiment, the center of the eccentric center C2, that is, the sector gear 120, in accordance with the rotation of the cam 130 is the eccentric arc portion located in the same direction as the eccentric shaft portion 132 and the eccentric cam portion 137 It is positioned on the same angle as the rotated angle of (133). That is, as the center C2 of the sector gear 120 rotates as the cam 130, the center C2 of the sector gear 120 has a radius of a circle whose radius is about the center C1 of the holder 110. Will have

The outer tooth 121 of the sector gear 120 is engaged with the inner tooth 111 of the holder 110 in accordance with the rotation of the cam 130 to revolve, and at the same time the outer tooth 121 and the inner tooth 111 The sector gear 120 rotates in a direction opposite to the idle direction according to the number of teeth.

According to the rotation of the sector gear 120, a side coupled to the unit gear, for example, a seatback (not shown), is rotated.

FIG. 6 shows a state in which the cam 130 is rotated 45 ° counterclockwise from the state of FIG. 5. As shown, in the present embodiment, as the eccentric arc portion 133 on the cam 130 side rotates 45 °, the sector gear 120 also rotates in contact with the inner tooth 111 of the holder 110. It can be seen that the center C2 also 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.

At this time, the outer circumferential surfaces of the clutch shoes 135 and 136 form a pair of wedge groove portions W1 and W2 circumferentially extending from the inner circumferential surface of the bearing 140 so as to be symmetrical with each other.

Each of the wedge groove portions W1 and W2 has a narrow side of the eccentric arc portion 133 and a wide side thereof.

On the other hand, the C-type elastic member 150 is accommodated in the space portion 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. do.

At this time, as shown in FIG. 5, the left end portion 151 of the C-type elastic member 150 is inserted into the wedge groove portion W1 on the left side, and the one end portion 152 on the right side is the wedge groove portion W2 on the right side. ) Is inserted.

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 counterclockwise rotation of the cam 130 around the C2 through the left clutch shoe 135, but the clockwise rotation generates friction force. It performs a one-way clutch function to prevent this. Similarly, the right end portion 152 of the C-shaped elastic member 150 allows clockwise rotation of the cam 130 around C2 through the right clutch shoe 136, but counterclockwise rotation generates friction force. It performs a one-way clutch function to prevent.

Accordingly, both ends 151 and 152 of the C-type elastic member 150 are a pair of one-way clutch portions, and when the sector gear 120 is impacted from the outside through a seat back, the cam 130 is moved to the sector gear ( By exerting a bearing force that prevents rotation in both directions, the seatback is prevented from turning over.

In particular, a clutch element for carrying out the function of such a pair of one-way clutch portions is achieved by a single C-type elastic member 150 as described above, whereby the effect of component reduction can be obtained.

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, all of these errors can be concentrated in the change in the radial width to the 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.

However, as described above, such as 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, or the like. Due to the presence of processing errors in the part, if all of these errors appear as a change in the width of the wedge grooves (W1, W2), it may cause a deviation of the operating force during the rotation operation of the cam 130.

That is, when the width of the wedge grooves W1 and W2 is changed due to the machining error according to the section in which the cam 130 is rotated, the cam 130 is easily (fast) even with the same operating force in the wide section. In the narrow section, the cam 130 may be difficult to rotate even with the same operating force.

Elastic pressing means such as U-shaped spring 160 is provided to eliminate the deviation of the operation force of the cam 130.

In FIG. 5, the U-shaped spring 160 is inserted between the outer C-shaped elastic member 150 and the inner boss 112 to press the C-shaped elastic member 150 outwardly, that is, in a radial direction.

As a result, both ends 151 and 152 of the C-type elastic member 150 are inserted into the wedge groove portions W1 and W2 in a state where the C-shaped elastic member 150 is slightly opened to the outside.

Accordingly, the depth at which both ends 151 and 152 are inserted into the wedge grooves W1 and W2 for locking the cam 130 is greatly shortened.

That is, the distance between the end portions 151 and 152 of the C-shaped elastic member 150 from the wedge grooves W1 and W2 is also shortened to unlock the cam 130.

Therefore, the unlocking of the cam 130 is more dependent on the opening of the C-shaped elastic member 150 to some extent for the unlocking, rather than on the width of the wedge grooves W1 and W2, resulting in As a result, a relatively constant rotational operating force is required during unlocking.

Therefore, even if there is a slight difference in the width of the wedge groove portions W1 and W2 due to machining errors between parts, the rotational force of the knob for unlocking the cam 130 does not depend greatly on the rotational section, but relatively. Can be kept constant.

On the other hand, the rotation operation of the cam 130 is achieved by the following principle.

That is, when the cam 130 is rotated in the counterclockwise direction by rotating the knob (not shown) coupled to the through hole 134, in FIG. 5 and FIG. By rotating clockwise, the sector gear 120 revolves 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, the radial length at one point in the space becomes larger and larger (see FIG. 5), so that the counterclockwise rotation of the eccentric cam portion 137 is C-type elastic member. It is not disturbed by the left end 151 of 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.

The dial recliner 100 described above is only an embodiment for explaining the present invention, but the scope of the present invention is not limited to the scope of the present invention, and the scope of the present invention is described in the following patents. It is determined by the claims and their equivalents.

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
137: eccentric cam portion 140: bearing
150: C type elastic members 151, 152: one-way clutch portion
160: U-shaped spring 170: housing

Claims (2)

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 at an outer circumferential surface thereof with an outer tooth portion engaged with the inner tooth portion of the holder to perform a rolling motion in the holder and have a circular receiving portion having a center eccentric from the center of the holder;
A bearing which is inserted into a receiving portion of the sector gear and is supported in a radial direction, and is accommodated in a state in which the boss is eccentrically spaced inside;
A central shaft portion inserted into the boss, an eccentric cam portion rotatably coupled to the inner circumferential surface of the bearing, and a pair of clutch shoes forming a wedge groove portion symmetrically with each other in the circumferential direction between the bearing A cam formed of;
A C-shaped elastic member accommodated between the bearing and the boss to form a pair of one-way clutch portions by having one end inserted into one wedge groove and the other end inserted into the other wedge groove; And
And an elastic pressing means received between the C-type elastic member and the boss to pressurize the C-type elastic member in a radial direction. The method of claim 1,
The elastic pressing means is a dial recliner, characterized in that the U-shaped spring.

Images