JPH0330040Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Technical Field) The present invention relates to a reclining device for adjusting the reclining angle of a vehicle seat or the like.

(Prior art) A first pinion is provided on the shaft for rotatably attaching the Atsupa arm to the lower arm,
The first pinion is configured to be rotatable by an operating handle, and one end of the second pinion rotatably supported on the upper arm side is engaged with the arcuate toothed portion provided on the lower arm; A reclining device is already known in which the first pinion is engaged with the external teeth of a gear plate, which engages with the other end of the second pinion and the central internal teeth.
In this type of device, when a load is applied to the seat back by an occupant, a considerably large force is applied to the meshing portion between the second pinion and the circular toothed portion of the lower arm. At this time, in the conventional device, an unacceptable shearing force acts on the teeth of the second pinion, resulting in damage or breakage.

(Purpose of the invention) The present invention has been made in view of these points, and its purpose is to provide a reclining device that can avoid damage or breakage of the second pinion.

(Structure of the invention) The present invention that achieves this object is configured such that a first pinion is provided on the shaft for rotatably attaching the upper arm to the lower arm, and the first pinion can be rotated by an operating handle. The arc toothed portion provided on the lower arm is engaged with an intermediate portion of a second pinion rotatably supported on the upper arm side, and one end of the second pinion is engaged with a central portion of the gear plate. A reinforcing plate is provided so that the internal teeth mesh with each other, the external teeth of the gear plate mesh with the first pinion, and the other end of the second pinion meshes with the central internal teeth. That is.

(Example) Hereinafter, an example of the present invention will be described in detail using the drawings.

In FIGS. 1 to 6, 1 is an upper arm, 2 is a lower arm, and 3 is a hinge shaft. A brake portion 3a located in the middle of the hinge shaft 3 is fitted and slid into contact with the inner circumferential surface of the hinge hole 2a of the lower arm 2. Also, this hinge shaft 3
One end thereof is rotatably inserted into an annular cushion 4 and a bush 5 (which are press-fitted and fixed to the upper arm 1). On the other hand, the other end of the hinge shaft 3 is rotatably inserted into a bush 8 press-fitted into the sub-plate 7, and its protruding serration portion 3b is inserted into the serration hole 9a of the pulley 9. It is prevented from coming off by a ring 10. This allows the hinge shaft 3
rotates while receiving a predetermined frictional force from peripheral members (lower arm 2, cushion 4, etc.). Further, a first pinion 3c is carved in the intermediate portion of the hinge shaft 3, and the external teeth 11a of the gear plate 11 are in circumscribed contact with the first pinion 3c. The gear plate 11 is also carved with internal teeth 11b, and one end of a second pinion 12a formed on the pinion shaft 12 is meshed with or press-fitted into the internal teeth 11b. The lower arm 2 has an arcuate elongated hole centered around the hinge hole 2a, and internal teeth are carved on the inner wall surface on the large diameter side to form an arcuate toothed portion 2b. An intermediate portion of the second pinion 12a of the pinion shaft 12 meshes with the arc toothed portion 2b. Furthermore, the inner tooth 29a at the center of the disk-shaped reinforcing plate 29 is meshed with or press-fitted into the other end of the second pinion 12a. As a result, the second pinion 1
2a is supported by a gear plate 11 and a reinforcing plate 29 at both ends. Note that, after one end of the pinion shaft 12 is rotatably inserted into the through hole 1a of the upper arm 1,
It is prevented from coming off by an E-ring 6, and the other end is prevented from coming off by an E-ring 13 after being inserted into the through hole 7a of the sub-plate 7. The cushion 4 has a function of preventing the pinion shaft 3 from rotating due to vibration.

14 is a handle shaft, and a first serration portion 14a provided in the middle thereof is a pulley 15.
The second serration portion 14b on the end side is inserted through the serration hole 15a of the operating handle 17 through the through hole 16a of the cover 16. And the operation handle 17
is prevented from coming off by a snap spring 18. The cylindrical portion 14c on the other end side of the handle shaft 14 is connected to the lower arm 2 via an eccentric holder 19.
installed on. The eccentric holder 19 consists of a concentric cylindrical part 19a for attachment to the lower arm 2 and an eccentric cylindrical part 19b that rotatably holds the handle shaft 14. A bolt with a washer 2 is inserted into the female thread provided on the inner cylindrical surface.
Fixing to the lower arm 2 is achieved by screwing in the concentric cylindrical portion 19a.
(Selected to be smaller than the plate thickness of lower arm 2).
A pair of opposing lateral grooves 19c are bored in the outer peripheral surface of the eccentric cylindrical portion 19b.
When the snap spring 21 is fitted into the horizontal groove 19c from the outside, the cylindrical portion 14 of the handle shaft 14
A snap spring 2 is inserted into the annular groove 14d provided in c.
1 is fitted into the handle shaft 14 to prevent the handle shaft 14 from coming off. Moreover, the eccentric cylindrical portion 19b
A parallel plane part (notch part) 19d is provided on the outer circumferential surface of the holder, and the cross-sectional outline is approximately oval in shape.As shown in FIG. , eccentric holder 19 at any angle
It is designed so that it can be rotated.

A belt 22 is wound around the pulleys 9 and 15 and is made of polyurethane or the like. Usually, a core material is used to increase the strength, and grooves are cut into the inner surface in a direction perpendicular to the direction of movement to prevent slipping. Of course, similar grooves are also carved on the outer peripheral surfaces of the pulleys 9 and 15. In order to prevent the belt 22 from coming off the pulleys 9 and 15, the pulleys 9 and 15 have flanges 9b and 15b on one side, respectively.
Further, flanges 23 and 2 of separate members are provided on the other surface so as to face the flanges 9b and 15b.
4 is fixed. In addition, 25 and 26 are rivets for riveting the sub-plate 7 to the upper arm 1;
7 and 28 are spacers.

The reclining angle adjustment operation in the embodiment configured as described above will be described next.

This adjustment operation is performed using the operating handle 17. That is, when the operating handle 17 is rotated, the pulley 15 is rotated, and this rotation is transmitted to the hinge shaft 3 via the belt 22 and the pulley 9, and the first
The pinion 3c rotates. This first pinion 3c
The rotation is transmitted to the pinion shaft 12 via the gear plate 11, causing the second pinion 12a to rotate. This rotation of the second pinion 12a is achieved by the second pinion 12a rolling against the arcuate toothed portion 2b of the lower arm 2, so that the pinion shaft 12 rotates against the hinge shaft 3 due to this rotation. Swings to the center. For this reason,
When the upper arm 1 is tilted, the inclination angle of the seat bag (not shown) attached to the upper arm 1,
That is, the reclining angle changes. Naturally, the direction in which the seat bag is tilted is determined by the direction in which the operating handle 17 is rotated. Incidentally, the handle operating force during this adjustment can be extremely small since the gear train when the upper arm 1 is viewed from the operating handle 17 is a reduction gear train. Also, to explain the locking when a load is applied to the seat back from the passenger side, this load is first converted into a force that attempts to rotate the second pinion 12a via the upper arm 1, and then the gear plate 11 and the second pinion 12a are rotated. The rotational force is transmitted to the brake section 3a via the first pinion 3c. The rotational force at this brake portion 3a is extremely small because it passes through the speed increasing gear train (when viewed from the second pinion 12a side). Therefore, this rotational force is smaller than the braking force that the brake portion 3a receives due to friction with surrounding members. Therefore, the seat back is in a locked state and will not tilt due to the load.

By the way, when the above-mentioned load is applied to the seat bag, a shearing force acts on the second pinion 12a as described above, but in the case of this configuration, the second pinion 12a
A gear plate 11 and a reinforcing plate 29 are installed at both ends of the
Since the teeth are meshed or press-fitted, the shearing force is shared even by the teeth that are not in mesh with the arcuate tooth section 2b of the lower arm 2. Therefore, the shearing force applied to the meshing teeth of the second pinion 12a is reduced. Furthermore, since both ends are supported by the plates 11 and 29, no force is applied in the torsional direction. For these reasons, the second pinion 12a will not be damaged or broken. Further, in this embodiment, the eccentric holder 19 can be set at any angle by loosening the bolt 20 and rotating the eccentric holder 19. Therefore, the distance between the pulleys 9 and 15 can be adjusted by twice the eccentricity S (see FIG. 5) of the eccentric cylindrical portion 19b in the eccentric holder 19 (ie, 2S). Therefore, when assembling the belt 22, the pulleys 9 and 1
By reducing the interval 5, assembly work can be easily performed. Of course, the tension can be adjusted after assembly by adjusting the distance between the pulleys 9 and 15 to a predetermined value. After this tension adjustment, if the eccentric holder 19 is fixed to the lower arm 2 again using the bolt 20, the desired belt tension can be maintained.

In addition, as a reclining angle adjustment mechanism, the operation handle 17 is fixed to the hinge shaft 3 itself without using the belt 22 or pulleys 9, 15 (the disadvantage is that the position of the operation handle 17 is limited and the operability is poor) ) may be adopted. or,
In the above embodiment, the cylindrical portion 19 is located on the eccentric holder 19 side.
b, and the cylindrical part 14 is provided on the handle shaft 14 side.
c is provided, but it may be the reverse.

(Effects of the Invention) As explained above, according to the present invention, the shearing force applied to the second pinion can be reduced, so damage or breakage to the second pinion can be avoided.

[Brief explanation of the drawing]

FIG. 1 is a schematic front view showing an embodiment of the present invention;
Figure 2 is a sectional view of AA in Figure 1, Figure 3 is a cross-sectional view of Figure 1.
BB sectional view, FIG. 4 is an exploded perspective view, FIG. 5 is an enlarged sectional view of the eccentric holder portion, and FIG. 6 is an explanatory diagram of angle adjustment of the eccentric holder. 1...Atsupa arm, 2...Lower arm, 3...
...Hinge shaft, 3c...1st pinion, 7...
...Subplate, 9, 15...Pulley, 11...
Gear plate, 12...Pinion shaft, 12
a...Second pinion, 14...Handle shaft, 16...Cover, 17...Operation handle, 1
9... Eccentric holder, 20... Bolt, 22...
Belt, 29...Reinforcement plate.

Claims (1)

[Scope of utility model registration request] A first pinion is provided on the shaft for rotatably attaching the Atsupa arm to the lower arm,
The first pinion is configured to be rotatable by an operating handle, and an intermediate portion of a second pinion rotatably supported on the upper arm side is engaged with a circular toothed portion provided on the lower arm. One end of the second pinion meshes with the inner teeth at the center of the gear plate, and the outer teeth of the gear plate mesh with the first pinion. A reclining device characterized by having a reinforcing plate that engages internal teeth.