阅读说明：本技术 交通工具座椅倾角调节装置 (Vehicle seat inclination angle adjusting device ) 是由 寺口博明 高田阳一 于 2019-02-26 设计创作，主要内容包括：在这个交通工具座椅倾角调节装置(4)中,棘轮(10)的环形突起(13)具有周向布置的第一区域(A1)、第二区域(A2)和第三区域(A3),并且棘轮的外侧表面具有第四区域(A4)。突起(13)被成形为使得第三区域(A3)比第二区域(A2)沿径向进一步向外延伸。结果,第四区域(A4)的与第三区域(A3)对应的部分比第四区域(A4)的与第二区域(A2)对应的部分沿径向进一步向外延伸。(In this vehicle seat reclining device (4), the annular protrusion (13) of the ratchet (10) has a first region (a1), a second region (a2), and a third region (A3) that are circumferentially arranged, and the outer side surface of the ratchet has a fourth region (a 4). The protrusion (13) is shaped such that the third region (A3) extends radially further outwards than the second region (a 2). As a result, the portion of the fourth region (a4) corresponding to the third region (A3) extends further outward in the radial direction than the portion of the fourth region (a4) corresponding to the second region (a 2).)

1. A vehicle seat reclining device, comprising:

a disc-shaped ratchet and a disc-shaped guide coaxially assembled in a relatively rotatable manner;

a locking mechanism disposed between the ratchet and the guide and configured to limit relative rotation between the ratchet and the guide; and

a retaining ring that retains an assembled state of the ratchet and the guide,

wherein the locking mechanism comprises: a plurality of pawls supported by the guide to be movable in a radial direction, the plurality of pawls being engaged with the ratchet when moved outward in the radial direction so as to restrict relative rotation between the ratchet and the guide; and a cam for moving the plurality of pawls outwardly or inwardly in the radial direction,

wherein the ratchet has: an annular protrusion at which an outer peripheral portion of the ratchet protrudes to one side in an axial direction; and an outer side surface portion configured to face the seat frame on the other side in the axial direction of the ratchet,

wherein the protrusion has: a first region in which a specific pawl of the plurality of pawls is allowed to move outward in the radial direction and to engage with the ratchet; a second region in which the specific pawl is prevented from moving outward in the radial direction and is engaged with the ratchet; and a third region in which another pawl is located when the specific pawl is in the second region, the first region, the second region, and the third region being arranged in the circumferential direction,

wherein the outer side surface portion has a fourth region configured to be in contact with and coupled to the seat frame, and

wherein the protruding portion has a shape in which the third region extends further outward in the radial direction than the second region, so that the fourth region has a shape in which a portion of the fourth region corresponding to the third region is wider outward in the radial direction than a portion of the fourth region corresponding to the second region.

2. The vehicle seat reclining device according to claim 1,

wherein the outer side surface portion has a projection that projects toward the other side in the axial direction so as to be fitted into the seat frame, the projection being provided on the fourth region, and

wherein the projection has a shape in which a length of the projection in the circumferential direction is equal to or smaller than a length of the third region in the circumferential direction.

Technical Field

The invention relates to a vehicle seat inclination angle adjusting device. More particularly, the present invention relates to a vehicle seat reclining device for adjusting a reclining angle of a seat back.

Background

As a vehicle seat reclining device of the related art, a device including a step-type lock mechanism capable of adjusting a backrest angle of a seat back at a constant pitch angle is known (patent document 1). The vehicle seat reclining device described above is configured as an engagement device that connects the seat back to the seat cushion in a state in which the angle of the seat back can be adjusted. Specifically, the vehicle seat reclining device includes: a ratchet and a guide which are made of a substantially disk-shaped metal member and which are assembled to be rotatable relative to each other; and a locking mechanism that locks relative rotation of the ratchet and the guide.

The above-described ratchet is coupled to the side frame by: a plurality of projections (so-called pins) formed to project from the outer side surface portion of the ratchet are fitted and welded into fitting holes formed in the side frame of the seat back.

Reference list

Patent document

Patent document 1: WO 2016/129423

Disclosure of Invention

Technical problem

In the related art, a part of the outer peripheral edge shape of the outer surface portion of the ratchet is recessed inward in the radial direction by half blanking to form a shape on the inner surface portion side. Further, the positions where some projections (pins) are formed and the welding spaces to the side frames are accumulated inward in the radial direction, which is disadvantageous in terms of strength. One of the objects of the present invention is to expand the coupling area of the ratchet to the seat frame outward in the radial direction in the vehicle seat reclining device.

Solution to the problem

[1] According to a first aspect of the present invention, a vehicle seat reclining device includes:

a disc-shaped ratchet and a disc-shaped guide coaxially assembled in a relatively rotatable manner;

a locking mechanism disposed between the ratchet and the guide and configured to limit relative rotation between the ratchet and the guide; and

a retaining ring that retains an assembled state of the ratchet and the guide, and

the locking mechanism includes: a plurality of pawls supported by the guide to be movable in a radial direction, the plurality of pawls being engaged with the ratchet when moving outward in the radial direction to restrict relative rotation between the ratchet and the guide; and a cam for moving the plurality of pawls outwardly or inwardly in the radial direction,

the ratchet wheel has: an annular protrusion at which an outer peripheral portion of the ratchet protrudes to one side in an axial direction; and an outer side surface portion configured to face the seat frame on the other side in the axial direction of the ratchet,

the protruding portion has: a first region in which a specific pawl of the plurality of pawls is allowed to move outward in the radial direction and to engage with the ratchet; a second region in which the specific pawl is prevented from moving outward in the radial direction and is engaged with the ratchet; and a third region in which another pawl is located when the specific pawl is in the second region, the first region, the second region, and the third region being arranged in the circumferential direction;

the outer side surface portion has a fourth region configured to be in contact with and coupled to the seat frame, and

the protruding portion has a shape in which the third region extends further outward in the radial direction than the second region, so that the fourth region has a shape in which a portion of the fourth region corresponding to the third region is wider outward in the radial direction than a portion of the fourth region corresponding to the second region.

According to the first aspect, in a fourth region (later-described coupling region) of the outer side surface portion of the ratchet wheel that couples with the seat frame, a portion corresponding to a third region (later-described other region) of the protrusion has a shape (later-described shape of the enlarged surface portion) that is wider outward in the radial direction than a portion corresponding to a second region (later-described free region). Therefore, the seat reclining device having such a configuration can enlarge the portion of the ratchet coupled to the seat frame to the outside in the radial direction, as compared with the seat reclining device in the related art.

[2] According to a second aspect of the present invention, in the above first aspect,

the outer side surface portion has a projection that projects toward the other side in the axial direction so as to be fitted into the seat frame, the projection being provided on the fourth region, and

the projection has a shape in which a length of the projection in the circumferential direction is equal to or smaller than a length of the third region in the circumferential direction.

According to the second aspect, it is possible to secure, in the fourth region (coupling region), a wide space in which the space around both ends in the circumferential direction of the protrusion (pin) is continuous with the space outside in the radial direction of the protrusion (pin). Therefore, it is possible to ensure the ratchet is coupled to a wider area of the seat frame.

Drawings

Fig. 1 is a perspective view showing a schematic configuration of a vehicle seat to which a vehicle seat reclining device according to a first embodiment is applied.

Fig. 2 is an exploded perspective view of a main part of fig. 1.

Fig. 3 is an exploded perspective view of fig. 2 viewed from the opposite side.

Fig. 4 is an exploded perspective view of a reclining device of a vehicle seat.

Fig. 5 is an exploded perspective view of fig. 4 viewed from the opposite side.

Fig. 6 is an outside view of the reclining device of a vehicle seat.

Fig. 7 is an inside view of the reclining device of a vehicle seat.

Fig. 8 is a front side view of the vehicle seat reclining device.

Fig. 9 is a sectional view taken along line IX-IX of fig. 1.

Fig. 10 is a sectional view taken along line X-X of fig. 8, showing a locked state of the vehicle seat reclining device.

Fig. 11 is a sectional view corresponding to fig. 10, showing an unlocked state of the vehicle seat reclining device.

Fig. 12 is a sectional view showing a state where the ratchet is turned from the state shown in fig. 11 to a free area.

Fig. 13 is a sectional view showing a state in which a locking operation of the vehicle seat reclining device is blocked from the state shown in fig. 12.

Fig. 14 is a sectional view showing a state where the ratchet is turned from the state shown in fig. 12 to an end position of the free area.

Fig. 15 is an enlarged view of the XV portion in fig. 9.

Fig. 16 is a sectional view showing a state in which the rotating cam is pressed against the guide member wall by being biased.

Fig. 17(a) to 17(d) are sectional views showing a variation of the locking operation of each pawl according to a variation of the rotational position of the ratchet wheel, divided into four cases.

Fig. 18(a) to 18(d) are schematic views showing a positional relationship between a ride projection of each pawl and a projection of a ratchet wheel in fig. 17(a) to 17 (d).

Fig. 19 is an outside view of each pawl.

Fig. 20 is an inside view of each pawl.

Detailed Description

Hereinafter, embodiments for implementing the present invention are described with reference to the drawings.

First embodiment

(schematic structure of seat reclining device 4)

First, the configuration of a vehicle seat reclining device 4 (hereinafter simply referred to as "device 4") according to a first embodiment will be described with reference to fig. 1 to 20. In the following description, directions such as front, rear, up, down, left, and right refer to the respective directions shown in the drawings. The "seat width direction" refers to the left-right direction of the seat 1.

As shown in fig. 1, the device 4 according to the present embodiment is applied to a seat 1 constituting a right-side seat of an automobile. The above-described device 4 is configured as a seat reclining adjustment mechanism that connects the seat back 2 serving as the backrest portion of the above-described seat 1 to the seat cushion 3 serving as the sitting portion in a state in which the backrest angle can be adjusted. Specifically, the above-described device 4 is provided between the above-described seat back 2 and seat cushion 3, thereby providing a pair of left and right devices 4. The device 4 is configured to fix or release the backrest angle of the seat back 2 by integrally switching between the locked state and the unlocked state.

Specifically, the above-described devices 4 are provided between respective lower end portions of side frames 2F forming left and right side frames of the above-described seat back 2 and respective reclining plates 3F on the outer sides in the seat width direction, the reclining plates 3F being connected to rear end portions of the left and right side frames of the seat cushion 3, so that the devices 4 can be relatively rotated or stopped coaxially with respect to each other (see fig. 2 and 3).

The above-described device 4 is normally held in a locked state in which the backrest angle of the seat back 2 is fixed. By an operation of pulling up the reclining lever 5 provided on the right side portion of the seat cushion 3 on the vehicle outer side, the device 4 is immediately released from the locked state, thereby switching to the unlocked state in which the backrest angle of the seat back 2 can be changed. After returning the above-described operation of pulling up the reclining lever 5, the device 4 is returned to the locked state again by being biased.

Here, a return spring 6 that always applies a spring biasing force to the seat back 2 in a direction in which the seat back 2 rotates to tilt forward is hooked between the side frames 2F on the left and right sides of the seat back 2 and the reclining plate 3F disposed on the outer sides of the side frames 2F. Due to the rotational biasing force of these return springs 6, by releasing the fixed state of the backrest angle via the above-described device 4, the seat back 2 is lifted to a position in contact with the back of the seated person, so that the backrest angle can be freely adjusted back and forth in accordance with the back-and-forth tilting movement of the seated person. According to this configuration, the seat back 2 is configured such that the back rest angle can be easily adjusted.

The seat back 2 is rotatable in the seat front-rear direction in a rotation region of about 180 degrees with respect to the seat cushion 3 described above between a forward tilting position where the seat back 2 is folded to the upper surface of the seat cushion 3 and a rearward tilting position where the seat back 2 is tilted substantially straight to the rear side. In the above-described rotation region, a rotation region of about 90 degrees from the upright position where the backrest angle of the seat back 2 is substantially straight with respect to the upper side to the above-described rearward-inclined position is set as a "locking region" in which the backrest angle of the seat back 2 returns to the fixed state when the upward pulling operation of the reclining lever 5 is released. Further, a rotation region of the backrest angle of the seat back 2 from the upright position to the forward tilting position is set as a "free region" in which the backrest angle of the seat back 2 is maintained in the released state without returning to the fixed state despite the release of the upward pulling operation of the reclining lever 5.

The above-described lock region and free region correspond to a lock region a1 and a free region a2 provided in the device 4 described later, respectively. By providing the above-described free region a2, when the reclining lever 5 is operated without a person sitting on the seat 1, once the seatback 2 is tilted to the position entering the free region a2 due to the above-described bias of the return spring 6, the seatback 2 is thereafter tilted to the forward tilting position even without continuing the operation of the reclining lever 5. Here, the locking region a1 corresponds to the "first region" of the present invention, and the free region a2 corresponds to the "second region" of the present invention.

As shown in fig. 2 and 3, in particular, the above-mentioned device 4 comprises: a ratchet 10 integrally coupled to an outer surface of the side frame 2F on each side of the seat back 2 described above; and a guide 20, the guide 20 being integrally coupled to an inner surface of the inclination adjustment plate 3F on each side. The device 4 is configured such that the backrest angle of the seat back 2 is fixed or released by locking or unlocking the relative rotation between the ratchet 10 and the guide 20. Here, the side frame 2F corresponds to a "seat frame" of the present invention.

(concrete constitution of device 4)

Hereinafter, a specific configuration of the pair of left and right devices 4 will be described in detail. Since the devices 4 have the same configuration and are symmetrical to each other, the configuration of one device disposed on the vehicle outer side (right side) shown in fig. 2 to 3 will be described as a representative in the following description.

As shown in fig. 4 and 5, the apparatus 4 includes: a ratchet 10 and a guide 20 of a substantially disk shape, the ratchet 10 and the guide 20 being assembled with each other in an axial direction; three pawls 30, the three pawls 30 being assembled between the ratchet 10 and the guide 20; a rotating cam 40, the rotating cam 40 being configured to move the three pawls inward and outward in a radial direction; a lock spring 50, the lock spring 50 being formed of a coil spring that biases the rotating cam 40 against the guide 20 in a direction that locks the rotational movement; and a substantially cylindrical outer peripheral ring 60, the outer peripheral ring 60 being mounted on outer peripheral portions of the ratchet 10 and the guide 20 so as to hold the ratchet 10 and the guide 20 in an assembled state in the axial direction. The ratchet 10, the guide 20, the three pawls 30, and the rotating cam 40 are configured to be hardened by being subjected to a quenching process after press-forming, thereby enhancing structural strength. Here, the above-described rotating cam 40 corresponds to a "cam" of the present invention. Hereinafter, the specific configuration of each member constituting the above-described apparatus 4 will be described in detail in turn.

(ratchet 10)

As shown in fig. 4, the ratchet 10 is formed by cutting one metal plate member into a substantially disc shape and half blanking at a position in the plate thickness direction (axial direction).

Specifically, the outer peripheral edge portion of the disc main body 11 of the above-described ratchet 10 is formed with a cylindrical portion 12, the cylindrical portion 12 protruding in a substantially cylindrical shape in an axial direction, which is a direction of attachment to a guide. Specifically, the above-described cylindrical portion 12 is formed by half blanking such that the outer peripheral edge portion of the disc main body 11 protrudes in two steps in the axial direction, and is formed into a stepped cylindrical shape of a cylindrical shape having inner and outer two steps, in which shape an intermediate cylindrical portion 13 is formed on the inner peripheral side, the intermediate cylindrical portion 13 being smaller than the cylindrical portion 12 in the axial direction, and protruding into a substantially cylindrical shape. Here, the above-described intermediate cylindrical portion 13 corresponds to a "protruding portion" of the present invention.

The inner peripheral surface of the cylindrical portion 12 described above is formed with inner peripheral teeth 12A, tooth surfaces of the inner peripheral teeth 12A facing inward in the radial direction, so that the inner peripheral teeth 12A are continuously arranged over the entire area in the circumferential direction. The above-described inner peripheral teeth 12A are formed in a tooth surface shape, and outer peripheral teeth 31 formed on an outer peripheral surface of each pawl 30 described later can be meshed with the inner peripheral teeth 12A by being pressed from the inside in the radial direction. Specifically, the above-described inner peripheral teeth 12A are configured such that the tooth faces are arranged in the circumferential direction at equal intervals of a pitch of 2 degrees apart from each other.

Further, the inner peripheral surface of the intermediate cylindrical portion 13 is formed with: three circumferential direction regions (region 13A, region 13B, and region 13C) in which an inner diameter from a center portion (central axis C) and a length in the circumferential direction are respectively provided; first and second projections 13D and 13E projecting inward in the radial direction from the boundaries of some of these regions; and a escaping recess 13F, the escaping recess 13F being outwardly recessed in the radial direction at the boundary position of the region 13C and the above-described second projection 13E.

Each of the region 13A, the region 13B, and the region 13C is formed in an inner peripheral surface shape that is curved to draw a concentric arc around a central portion (central axis C). Specifically, the regions 13A and 13C are formed in an inner peripheral surface shape having a larger inner diameter than the region 13B, and the regions 13A and 13C are formed in an inner peripheral surface shape having the same inner diameter.

As shown in fig. 10, 17(a) and 18(a), when a main pawl P1 of three pawls 30, which will be described later, is arranged to coincide with a region 13A in the circumferential direction by rotation of the ratchet 10, the above-mentioned region 13A constitutes a locking region a1 of the main pawl P1, the locking region a1 allowing the main pawl P1 to move outward in the radial direction to engage with the inner peripheral teeth 12A of the ratchet 10 and be locked. Here, the above-described primary pawl P1 corresponds to the "specific pawl" of the present invention.

Further, when the primary pawl P1 is arranged to coincide with the above-described region 13A in the circumferential direction, the above-described regions 13B and 13C serve as other regions A3 arranged to coincide with the remaining two secondary pawls P2 of the three pawls 30 in the circumferential direction, so that the secondary pawls P2 are allowed to move to engage with the inner peripheral teeth 12A of the ratchet 10. Here, the other area a3 corresponds to the "third area" of the present invention.

However, as shown in fig. 12, when the above-described main pawl P1 is arranged to coincide with the region 13B in the circumferential direction by the rotation of the ratchet 10, the region 13B serves as a free region a2 of the main pawl P1, thereby preventing the main pawl P1 from moving outward in the radial direction to engage with the inner peripheral teeth 12A of the ratchet 10 on the path as shown in fig. 13, 17(B) and 18 (B). Here, each of the above-described secondary pawls P2 corresponds to "another pawl" of the invention.

When the main pawl P1 is arranged to coincide with the above-described region 13B in the circumferential direction, the above-described region 13C and the region 13A serve as other regions A3 arranged to coincide with the remaining two sub pawls P2 in the circumferential direction, so that the movement of each sub pawl P2 in synchronization with the movement of the above-described main pawl P1 escapes from these regions.

That is, in the intermediate cylindrical portion 13 of the ratchet 10 described above, the above-described region 13A constitutes a locking region a1 (see fig. 10, 17(a), and 18(a)) that allows the locking operation of the main pawl P1, while the region 13B constitutes a free region a2 (see fig. 13, 17(B), and 18(B)) that blocks the locking operation of the main pawl P1 by riding and that the ratchet 10 can freely rotate in the circumferential direction while maintaining the unlocked state.

As shown in fig. 10, 17(a) and 18(a), when the primary pawl P1 is arranged to coincide with the region 13A in the circumferential direction as described above, the region 13B and the region 13C function as the other region A3 alone, so that the remaining two secondary pawls P2 are allowed to perform a locking operation in synchronization with the movement of the primary pawl P1. Further, as shown in fig. 13, 17(B) and 18(B), when the above-described main pawl P1 is arranged to coincide with the region 13B in the circumferential direction by the rotation of the above-described ratchet 10, the region 13C and the region 13A function as the other region A3 alone, so that the locking operation of the remaining two sub-pawls P2 in synchronization with the movement of the main pawl P1 is blocked halfway.

As described above, the intermediate cylindrical portion 13 of the ratchet 10 is controlled to allow and block the locking operation of the main pawl P1 by the above-described regions 13A and 13B, and the intermediate cylindrical portion 13 of the ratchet 10 is configured such that the movements of the remaining two sub pawls P2 synchronized with the movement of the main pawl P1 can escape through the other region (the other region A3) where the remaining two sub pawls P2 are located at this time.

In the case where the above-described main pawl P1 is pushed outward in the radial direction at the halfway point and is accidentally pressed against the step between the region 13A and the region 13B in the circumferential direction when moving from the locking region a1 (region 13A) to the free region a2 (region 13B) by the rotation of the ratchet 10 (i.e., in the case of the arrangement shown in fig. 17(B) and 18(B)), the first projection 13D and the second projection 13E are used to simultaneously contact with the two sub-pawls P2 as shown in fig. 17(c) and 18(c) so as to distribute the load caused thereby to the other two sub-pawls P2, rather than concentrating only on the main pawl P1.

That is, when the above-described primary pawl P1 is pressed against the step between the region 13A and the region 13B in the circumferential direction due to the rotation of the ratchet 10, the above-described first projection 13D and second projection 13E are formed at positions where the first projection 13D and second projection 13E are pressed against the remaining two secondary pawls P2 in the circumferential direction.

As shown in fig. 14, 17(d) and 18(d), when the above-described main pawl P1 is moved to an end position in the circumferential direction on the area 13B as the free area a2 due to the rotation of the ratchet 10, the escape recess 13F is configured to be disengaged from the riding state so that the main pawl P1 can be engaged with the inner peripheral teeth 12A of the ratchet 10 at that position. By escaping the recess 13F, the ratchet 10 is inclined downward to the end position of the free area a2 (i.e., the forward inclined position in which the seat back 2 described above with reference to fig. 1 is folded onto the upper surface of the seat cushion 3), so that the device 4 is locked at this position, and the seat back 2 can be switched to the state of stopping rotation. As a result, the seat back 2 can be locked in the forward tilted position so as not to be loosened.

As shown in fig. 4 and 5, a through hole 11A penetrating in a circular hole shape is formed at a central portion (on the central axis C) of the disc main body 11 of the above-described ratchet 10. The operation pin 5A inserted and mounted in a center portion (on the center axis C) of the rotating cam 40 described later is inserted through the through hole 11A from the outside in the axis direction in a freely rotatable state. Further, as shown in fig. 5, on the outer surface of the disk main body 11 of the above-described ratchet 10, projections (hereinafter referred to as "pins 14") that project by being pushed out in an arc shape in the axial direction are formed at three positions in the circumferential direction, which are positions that are arranged on the same circumference around the center portion (on the center axis C) of the disk main body 11.

The above-described pin 14 is formed in such a manner that one pin is accommodated in each of the formation regions in the circumferential direction in which the region 13A, the region 13B, and the region 13C of the above-described intermediate cylindrical portion 13 are formed. As shown in fig. 3, the ratchet 10 having the above-described configuration is assembled in such a manner that the outer surface of the disc main body 11 of the ratchet 10 is brought into surface contact with the outer surface of the side frame 2F of the above-described seat back 2, and the contact portion therebetween is welded, so that the ratchet 10 is integrally coupled to the side frame 2F of the seat back 2 (welded portion W).

Specifically, the above-described ratchet 10 is assembled in a state in which the three pins 14 formed on the outer surface of the disc main body 11 are fitted respectively into the three fitting holes 2Fa formed correspondingly in the side frame 2F of the seat back 2 and penetrating in a substantially arc shape, and the peripheral areas (coupling areas a4) of these fitted portions are joined and coupled by laser welding in a state of surface contact with the side frame 2F (welded portion W).

More specifically, the outer surface of the disc main body 11 of the above-described ratchet 10 is formed with the coupling region a4, which is a4 that abuts on the side frame 2F in a surface contact state, and is laser-welded on the outer side in the radial direction and on both sides in the circumferential direction of the region where the three pins 14 are formed. As shown in fig. 7, the above-described coupling areas a4 are configured such that the area 13A and the area 13C of the intermediate cylindrical portion 13 formed on the outer peripheral edge of the corresponding coupling area a4 are located on the outer side in the radial direction than the area 13B. Therefore, the coupling region a4 is configured such that a region of the formation region in the circumferential direction in which the region 13A and the region 13C are formed each has an enlarged surface portion 11B, the area of which enlarged surface portion 11B is enlarged in the radial direction compared with the region of the formation region in the circumferential direction in which the region 13B is formed. Here, the coupling region a4 corresponds to the "fourth region" of the invention.

According to such a configuration, the outer surface of the disc main body 11 of the ratchet 10 described above is configured such that the two coupling regions a4 each having the enlarged surface portion 11B in the respective forming regions in the circumferential direction in which the region 13A and the region 13C are formed to be firmly welded to the side frame 2F in such a manner as to abut more widely toward the outside in the radial direction, as compared with one coupling region a4 of the forming regions in the circumferential direction in which the region 13B is formed.

More specifically, the welding of the outer surface of the disc main body 11 of the ratchet 10 to the side frame 2F described above is performed in such a manner that each pin 14 is surrounded in a C-shape on both side areas in the circumferential direction from the outer area in the radial direction, so that a weld bead (weld portion W) is inserted. The side frame 2F is formed with a passage hole 2Fb that allows the operating pin 5A to pass through toward the outside in the axial direction, the operating pin 5A passing through a through hole 11A formed at the center portion (on the center axis C) of the ratchet 10.

(guide 20)

As shown in fig. 5, the guide 20 is formed by cutting a metal plate member into a substantially disc shape having an outer diameter slightly larger than that of the ratchet 10 and half blanking in a position in the plate thickness direction (axial direction).

Specifically, on the outer peripheral edge portion of the disc main body 21 of the above-described guide 20, a cylindrical portion 22 is formed to protrude in a substantially cylindrical shape in the axial direction, which is the direction of attachment to the ratchet 10. The cylindrical portion 22 is formed such that the inner diameter of the cylindrical portion 22 is slightly larger than the outer diameter of the cylindrical portion 12 of the ratchet 10 described above. As shown in fig. 9, the above-described guide 20 is provided such that the cylindrical portion 12 of the above-described ratchet 10 is inserted into the cylindrical portion 22 of the guide 20 in the axial direction.

Thus, the guide 20 and the ratchet 10 are assembled in a state in which their respective cylindrical sections 22, 12 are loosely fitted to each other inward and outward in the radial direction, so that the relative rotation between the cylindrical sections 22, 12 can be achieved in a state of being supported inward and outward. Then, the above-mentioned guide 20 is installed in the following state: an outer peripheral ring 60, which will be described later, spans from the outer peripheral side between the cylindrical portion 22 and the cylindrical portion 12 of the ratchet 10 described above, so that the guide 20 is assembled while the guide 20 is prevented from falling off from the ratchet 10 in the axial direction via the outer peripheral ring 60 (see fig. 2 and 3 and fig. 6 to 9).

As shown in fig. 5, guide walls 23 are formed at three positions in the circumferential direction on the inner surface of the disc main body 21 of the above-described guide 20, the guide walls 23 being formed by being pushed out in a half die-cut shape so as to project in a substantially fan-like shape in the axial direction, which is the direction of assembly to the ratchet 10. These guide wall 23 are formed such that respective outer circumferential surfaces of the guide wall 23 in the radial direction are curved to draw arcs of concentric circles drawn around a central portion (central axis C) thereof. Each of the above-mentioned guide walls 23 is provided to be loosely fitted into the cylindrical portion 12 of the ratchet 10, which ratchet 10 is assembled in the cylindrical portion 22 of the above-mentioned guide 20.

By forming the above-described guide wall 23, a pawl accommodating groove 24A is formed in an area in the arrangement in the circumferential direction of the guide wall 23 on the inner surface of the above-described tray main body 21, so that each of three pawls 30 described later can be provided so as to be slidable inward and outward in the radial direction. Further, a cam receiving groove 24B is formed in a central area on the inner surface of the disc main body 21 surrounded by the above-described guide wall 23, so that a rotating cam 40 described later can be provided to rotate axially.

As shown in fig. 10 and 11, the above-described guide wall 23 is applied to the respective pawls 30 correspondingly disposed in the above-described pawl accommodating grooves 24A so as to face each other from both sides in the circumferential direction by the restricting surfaces 23A, the restricting surfaces 23A being both side surfaces in the circumferential direction that face each pawl accommodating groove 24A, and configured to support each pawl 30 from both sides in the circumferential direction so as to guide each pawl 30 to be slidable only inward and outward in the radial direction.

Further, the above-described guide piece wall 23 is applied to the rotating cams 40 provided in the above-described cam accommodating groove 24B so as to face each other from the outside in the radial direction by a support surface 23B, which is an inner circumferential surface in the radial direction that faces the cam accommodating groove 24B, and is configured to support the rotating cams 40 from the outside in the radial direction so as to guide the rotating cams 40 to be rotatable only in the circumferential direction at the center portion (on the center axis C) on the disk main body 21 of the guide piece 20.

As shown in fig. 5, a play packing pin 21C is formed in a formation region of the pawl accommodating groove 24A in which the primary pawl P1 is provided on the inner surface of the disc main body 21 of the above-described guide 20, the play packing pin 21C being inserted into the wedge-shaped play packing hole 35 formed in the primary pawl P1 so as to protrude in a columnar shape in the axial direction. As shown in fig. 11, when the above-described primary pawl P1 is pulled inward in the radial direction and does not engage with the inner peripheral teeth 12A of the ratchet 10, the above-described play filling pin 21C is located in the outer region in the radial direction of the wedge-shaped play filling hole 35, in which the hole width is wide and the movement of the primary pawl P1 is not blocked.

However, as shown in fig. 10, as the primary pawl P1 is pushed outward in the radial direction and engages with the inner peripheral teeth 12A of the ratchet 10, the above-described play filler pin 21C is pressed into the inner region in the radial direction in which the hole width in the wedge-shaped play filler hole 35 of the primary pawl P1 is narrow, so that the play filler pin 21C can be switched to a state in which play of the primary pawl P1 in the circumferential direction is prevented. According to this configuration, the primary pawl P1 meshes with the inner peripheral teeth 12A of the ratchet 10 in a state in which play in the circumferential direction is prevented, and the ratchet 10 and the guide 20 are locked via the primary pawl P1 in a state in which play in the circumferential direction is prevented therebetween.

As shown in fig. 4 and 5, each of the above-described guide walls 23 is formed with a floating island-shaped boss portion 23C, which boss portion 23C is pushed out in a half die-cut shape toward the side opposite to the axial direction as the direction of assembly to the ratchet 10 at an intermediate portion in which a peripheral edge of a protruding area is left, the shape of which is enlarged in the circumferential direction and the radial direction. Each boss portion 23C is formed in the manner as described above, so that each guide piece wall 23 is configured to have a high structural strength capable of firmly supporting each pawl 30 from both sides in the circumferential direction without reducing the contact area with each pawl 30 to support each pawl 30 from both sides in the circumferential direction by the restricting surfaces 23A.

Further, at a central portion (on the central axis C) of the tray main body 21 of the above-described guide 20, a through hole 21A penetrating in a substantially circular hole shape is formed, and a lock spring 50, which will be described later, is accommodated in this through hole 21A. The above-mentioned through hole 21A is formed with a hanging hole 21Aa extending in an elongated hole shape toward the outside in the radial direction from a part of the hole shape of the through hole 21A. The outer end portion 52 of the locking spring 50 provided in the above-described through hole 21A is fitted into the hanging hole 21Aa in the axial direction so as to be integrally fixed in the circumferential direction.

As shown in fig. 4, on the outer surface of the disc main body 21 of the above-described guide 20, pins 21B are formed at three positions in the circumferential direction, the pins 21B protruding in a substantially cylindrical shape in the axial direction. Each of these pins 21B is formed in such a manner as to be pushed out one by one in the axial direction on the outer surface of the above-mentioned disc main body 21 in a region corresponding to the back side of the above-mentioned corresponding pawl accommodating recess 24A.

As shown in fig. 2, the guide 20 having the above-described configuration is in a state of being firmly and integrally coupled to the inclination adjustment plate 3F by a pin 21B protruding from the outer surface of the above-described tray main body 21, the pin 21B being fitted into and welded with a corresponding fitting hole 3Fa formed in the inclination adjustment plate 3F. The above-described inclination adjusting plate 3F is formed with a passage hole 3Fb that allows the operating pin 5A to pass through toward the outside in the axial direction, the operating pin 5A passing through a through hole 21A formed at the center portion (on the center axis C) of the above-described guide 20.

(ratchet 30)

As shown in fig. 4 and 5, the three pawls 30 are individually formed by cutting one sheet metal member into a substantially rectangular shape and half blanking in a position in the sheet thickness direction (axial direction). Specifically, each of the pawls 30 described above has a shape in which an offset surface portion 30B forming a region on the inner peripheral side of the pawl in the radial direction is pushed out in the axial direction (the axial direction is a direction of assembly to the ratchet 10) by an amount corresponding to substantially a plate thickness in a half die cut shape with respect to a main body surface portion 30A forming a region on the outer peripheral side.

Further, a specific one of the three pawls 30 is configured as a primary pawl P1, the primary pawl P1 having a partially different shape from the other two secondary pawls P2 so as to be distinguished in function. The specific differences will be described later.

As shown in fig. 10 and 11, each of the above-described pawls 30 is provided so as to be accommodated one by one in a corresponding pawl accommodating recess 24A formed on the inner surface of the tray main body 21 of the above-described guide 20. With this arrangement, each pawl 30 is set to the following state: each pawl 30 is supported in a planar shape from both sides in the circumferential direction by the restricting surface 23A of the guide wall 23 (the restricting surface 23A faces the corresponding pawl accommodating recess 24A from both sides in the circumferential direction), and is supported so as to be movable only inward and outward in the radial direction along the restricting surface 23A.

Specifically, as shown in fig. 9, when each of the above-described pawls 30 is disposed in the above-described corresponding pawl accommodating recess 24A, the body surface portion 30A of the pawl 30 is disposed so as to abut against the inner surface of the tray body 21 of the guide 20. Thus, each pawl 30 is disposed such that the inner peripheral teeth 12A of the cylindrical portion 12 of the ratchet 10 assembled in the cylindrical portion 22 of the above-described guide 20 face each other in the radial direction at a position on the outer side of the body surface portion 30A in the radial direction.

Further, the offset surface portion 30B of each of the pawls 30 is provided so as to be spaced apart from the inner surface of the disc main body 21 of the guide 20 in the axial direction and so as to coincide with the intermediate cylindrical portion 13 of the ratchet 10 in the axial direction.

As shown in fig. 4, on the outer peripheral surface in the radial direction of the main body surface portion 30A of each of the above-described pawls 30, there are formed outer peripheral teeth 31 whose tooth surfaces face outward in the radial direction, which are shaped so as to be continuously arranged over the entire area in the circumferential direction. An outer peripheral surface in the radial direction, on which the outer peripheral teeth 31 of each of the pawls 30 described above are formed, is formed into a curved surface shape along an inner peripheral surface of the cylindrical portion 12, on which the inner peripheral teeth 12A of the ratchet 10 are formed.

According to this configuration, the outer peripheral teeth 31 of each pawl 30 are pressed against the inner peripheral teeth 12A of the ratchet 10 from the inner side in the radial direction, so that the entire teeth are engaged with the inner peripheral teeth 12A of the ratchet 10. Specifically, as with the inner peripheral teeth 12A, the outer peripheral teeth 31 of each pawl 30 are configured such that the tooth surfaces are arranged in the circumferential direction at equal intervals of a pitch of 2 degrees apart from each other.

However, more strictly, referring to fig. 10, the outer peripheral teeth 31 of each pawl 30 described above are formed in such a manner that the tooth surface at the center in the circumferential direction enters the inner peripheral teeth 12A of the ratchet 10 and meshes with the inner peripheral teeth 12A deepest, and the tooth height becomes smaller as the depth of entry with respect to the inner peripheral teeth 12A of the ratchet 10 gradually decreases toward both end sides in the circumferential direction.

According to this configuration, in each pawl 30, in addition to the tooth surface at the center position where the tooth surface is oriented straight in its entering direction, other tooth surfaces whose directions are inclined from the same center position toward both end sides in the circumferential direction in a direction different from the entering direction can be appropriately engaged with the tooth surface of the corresponding inner peripheral tooth 12A of the ratchet 10 by the movement of each pawl 30 toward the outside in the radial direction without being replaced. The specific tooth surface shape of the peripheral teeth 31 is the same as that disclosed in ｃA document such as JP- ｃA-2015-29635, and thus ｃA detailed description thereof will be omitted.

According to such a configuration, when the outer peripheral teeth 31 are engaged with the inner peripheral teeth 12A of the ratchet 10, each pawl 30 can receive the action of the biasing force so that the entirety thereof is pushed and inclined in any one of the circumferential directions by the action of the pressing force from the inner side in the radial direction with the deepest engagement center position in the circumferential direction as the fulcrum. However, when the primary pawl P1 is to be engaged with the ratchet 10, the above-described action is appropriately suppressed by the action of pressing the play filling pin 21C provided on the guide 20 into the wedge-shaped play filling hole 35 (in which play is filled in the circumferential direction).

As shown in fig. 9, each of the pawls 30 described above is provided in such a manner that a rotary cam 40, which will be described later, provided at a central portion (on the central axis C) of the guide 20 faces the radial direction in a region at the inner side in the radial direction surrounded by the body surface portion 30A. With this arrangement, each pawl 30 is configured such that the body surface parts 30A are arranged side by side at positions on the outer side in the radial direction of the rotating cam 40, and the offset surface parts 30B are arranged to coincide with the rotating cam 40 in the axial direction.

Here, as shown in fig. 5, the inner peripheral surface of the main body surface portion 30A of each of the pawls 30 described above is formed with a pressed surface portion 32, the pressed surface portion 32 faces the rotating cam 40 described above in the radial direction, and the pressed surface portion 32 receives a force pressed from the inside to the outside in the radial direction as the rotating cam 40 rotates. Further, a pull-in hole 33 is formed at an intermediate portion of the offset surface portion 30B of each of the above-described pawls 30, and this pull-in hole 33 penetrates in the axial direction, so as to be operated such that, with the rotation of the rotary cam 40, a corresponding pull-in pin 42 formed on the above-described rotary cam 40 is inserted in this pull-in hole 33 and pulled inward in the radial direction. Further, at an intermediate portion of the main body surface portion 30A of each of the above-described pawls 30, a riding projection 34 is formed, and this riding projection 34 is pushed out in the same axial direction as the offset surface portion 30B in a half die cut shape.

As shown in fig. 10, the above-described rotating cam 40 is rotated in the counterclockwise direction in the drawing by a spring biasing force of a later-described lock spring 50 (this lock spring 50 is hooked between the rotating cam 40 and the guide 20), so that the pressed surface portion 32 of each of the above-described pawls 30 is pressed from the inside to the outside in the radial direction by the corresponding pressing portion 44 formed on the outer circumferential surface portion of the rotating cam 40. By the above pressing, the outer peripheral teeth 31 of each pawl 30 are pressed against the inner peripheral teeth 12A of the above ratchet 10 to be engaged with each other, and are held in such an engaged state. As a result, the pawls 30 are integrally coupled to the ratchet 10 in the circumferential direction, and the relative rotation between the ratchet 10 and the guide 20 is locked via each pawl 30.

Further, as shown in fig. 11, by the operation of the above-described reclining lever 5, the above-described rotating cam 40 is rotated in the clockwise direction as shown in the drawing against the spring biasing force of the locking spring 50, so that the pull-in hole 33 of each of the above-described pawls 30 is pulled inward in the radial direction by the corresponding pull-in pin 42 of the rotating cam 40 inserted therein. By the above pulling, the outer peripheral teeth 31 of each pawl 30 are not meshed with the inner peripheral teeth 12A of the above ratchet 10, and are held in this state (unlocked state). As a result, the above-described rotation-locked state between the ratchet 10 and the guide 20 is released.

As shown in fig. 9, the riding projection 34 of each of the above-described pawls 30 is pushed out to the same position in the same axial direction as the offset surface portion 30B of each of the above-described pawls 30 in a half die cut shape, and an outer peripheral surface portion 34A of the riding projection 34 is disposed so as to face the inner peripheral surface of the intermediate cylindrical portion 13 of the above-described ratchet 10 in the radial direction. As shown in fig. 10, 17(a) and 18(a), when the rotational position of the ratchet 10 with respect to the guide 20 is in the state of the above-described lock region a1, even if the above-described each pawl 30 is pushed outward in the radial direction by the rotating cam 40, the ride projection 34 of the above-described each pawl 30 is not pressed against the inner peripheral surface of the intermediate cylindrical portion 13 of the ratchet 10, so that the movement of each pawl 30 that is engaged with the inner peripheral teeth 12A of the ratchet 10 is not blocked.

However, as shown in fig. 13, 17(b) and 18(b), by changing the above-described rotational position of the ratchet 10 with respect to the guide 20 to the above-described state of the free area a2, when the above-described each pawl 30 is pushed outward in the radial direction by the rotating cam 40, the ride projection 34 of the above-described each pawl 30 is pressed against the inner circumferential surface of the intermediate cylindrical portion 13 of the ratchet 10 to ride thereon, so that the movement of each pawl 30 that meshes with the inner circumferential teeth 12A of the ratchet 10 is stopped at the intermediate position.

Specifically, the riding projection 34 of each of the pawls 30 described above is configured such that the diametrical dimension from the center portion (on the center axis C) of the guide 20 to the outer peripheral surface portion 34A of the primary pawl P1 is different from the other two secondary pawls P2, that is, the formation positions in the radial direction are different from each other. Specifically, the ride projections 34 of the primary pawl P1 are formed at positions that project further outward in the radial direction than the ride projections 34 of the other two secondary pawls P2.

As shown in fig. 10, 17(a) and 18(a), when the ride projection 34 of the above-described main pawl P1 is arranged to coincide with the region 13A (locking region a1) of the intermediate cylindrical portion 13 of the ratchet 10 in the circumferential direction, even if the ride projection 34 is pushed outward in the radial direction by the rotating cam 40, the ride projection 34 is not pushed out to a position riding on the region 13A, so that the movement of the main pawl P1 engaging with the inner peripheral teeth 12A of the ratchet 10 is not blocked.

At this time, the ride projections 34 of the other two secondary pawls P2 are formed at positions inward in the radial direction than the ride projections 34 of the above-described primary pawl P1, so that even if these ride projections 34 are arranged to coincide in the circumferential direction with the region 13B and the region 13C (other region A3) projecting more inward in the radial direction than the above-described region 13A, respectively, the ride projections 34 are not pushed out to positions riding on the regions 13B and 13C when pushed outward in the radial direction by the rotating cam 40, and therefore, the movement of each secondary pawl P2 meshing with the inner peripheral teeth 12A of the ratchet 10 is not blocked.

Further, as shown in fig. 13, 17(B) and 18(B), when the ride projection 34 of the above-described main pawl P1 is arranged to coincide with the region 13B (free region a2) of the intermediate cylindrical portion 13 of the ratchet 10 in the circumferential direction, the ride projection 34 is pushed outward in the radial direction by the rotating cam 40 to ride on the region 13B, so that the movement of the main pawl P1 that is engaged with the inner peripheral teeth 12A of the ratchet 10 is stopped at the intermediate position.

At this time, however, even if the ride projections 34 of the other two secondary pawls P2 are arranged to coincide with the corresponding regions 13C and 13A (other regions A3), respectively, in the circumferential direction, the ride projections 34 are not pushed out to the positions riding on the regions 13B and 13C when pushed outward in the radial direction by the rotating cam 40, so that the movement of each secondary pawl P2 toward the outside in the radial direction is not stopped at the intermediate position.

Even with this configuration, the movement of the secondary pawl P2 toward the outer side of the primary pawl P1 in the radial direction is stopped at the intermediate position, so that the rotation of the rotating cam 40 is also stopped accordingly, and the secondary pawl P2 is not pushed further outward in the radial direction so as to be held together with the primary pawl P1 in the unlocked state in which the secondary pawl P2 and the primary pawl P1 are prevented from being pressed against the inner peripheral teeth 12A of the ratchet 10. Each of the ride projections 34 formed on the above-described two secondary pawls P2 has a chamfered inclined surface 34B at a corner portion on one end side in the circumferential direction on its outer peripheral surface portion 34A.

From the state shown in fig. 13, 17(B) and 18(B) in which the ride projection 34 of the above-described main pawl P1 rides on the free region a2 (region 13B) of the ratchet 10 and the ride projection 34 of the sub pawl P2 is located on the region 13C and the region 13A, respectively, when the ratchet 10 rotates in the direction in which the ratchet 10 returns from the free region a2 to the locking region a1 without operating the reclining lever 5 (when the seat back 2 is lifted to the rear side), each of the above-described inclined surfaces 34B functions as a escape portion that allows the ride projection 34 of the sub pawl P2 to pass in the circumferential direction while escaping to the outside in the radial direction through the tilt guide so as not to abut on the first boss 13D and the second boss 13E in the circumferential direction.

Further, as shown in fig. 4 and 5, in the body surface portion 30A of the above-described primary pawl P1, the play filling hole 35 is formed in an intermediate portion, the play filling hole 35 penetrating in a shape in which the hole shape is tapered from the outside to the inside in the radial direction, the intermediate portion being separated from the formation region of the ride projection 34 in the circumferential direction. As shown in fig. 11, the above-described play filling hole 35 is provided such that, when the above-described primary pawl P1 is provided on the guide 20, a play filling pin 21C protruding from the inner surface of the disc main body 21 of the guide 20 is inserted into this play filling hole 35. With such an arrangement, when the above-described primary pawl P1 is in the unlocked state before meshing with the inner peripheral teeth 12A of the ratchet 10, the play packing hole 35 does not block the movement of the primary pawl P1, with the play packing pin 21C located in the region where the hole width is wide on the outer side in the radial direction.

However, as shown in fig. 10, as the above-described primary pawl P1 is pushed outward in the radial direction and engages with the inner peripheral teeth 12A of the ratchet 10, the above-described play filling hole 35 is configured such that the play filling pin 21C is pressed into a region where the inner hole width in the radial direction is narrow, and can be switched to a state in which play of the primary pawl P1 in the circumferential direction is prevented. According to this configuration, the primary pawl P1 meshes with the inner peripheral teeth 12A of the ratchet 10 in a state in which play in the circumferential direction is prevented, and the ratchet 10 and the guide 20 are locked in a state in which play in the circumferential direction between the ratchet 10 and the guide 20 is prevented via the primary pawl P1.

As shown in fig. 4 and 5 and fig. 19 and 20, each of the pawls 30 described above is formed such that the offset surface portion 30B and the ride-on projection 34 are respectively pushed out in the half-blanked shape in the same axial direction with respect to the main body surface portion 30A, thereby spacing the offset surface portion 30B and the ride-on projection 34 from each other in the radial direction. At this time, the offset surface portion 30B of each pawl 30 is formed such that a quality control surface Q for imparting accuracy to the formed surface obtained by half blanking is provided not on the outer peripheral surface portion side of the main body surface portion 30A which is pushed out in a half blanking shape and faces the outer side in the radial direction but on the inner peripheral surface portion (pressed surface portion 32) side of the main body surface portion 30A which is formed by half blanking in a manner to face the inner side in the radial direction. According to this configuration, each pawl 30 is configured such that the pressed surface portion 32 is accurately formed.

Further, the riding projection 34 of each pawl 30 is formed such that a quality control surface Q for imparting accuracy to a molded surface obtained by half blanking is provided on the outer peripheral surface portion 34A side which is pushed out in a half-blanked shape and faces the outside in the radial direction. According to such a configuration, each pawl 30 is configured such that the outer peripheral surface portion 34A and the inclined surface 34B are accurately formed. As described above, each of the pawls 30 is formed such that the offset surface portion 30B and the ride-on projection 34 are respectively pushed out in the half-blanked shape with respect to the main body surface portion 30A, thereby spacing the offset surface portion 30B and the ride-on projection 34 from each other in the radial direction, so that the quality control surface Q can be provided on the front side and the back side to improve the accuracy of the molding surface.

Specifically, the pressed surface portion 32 of each pawl 30 described above is configured such that each area separated from the formation position of the ride projection 34 on both sides in the circumferential direction is pressed from the inner side in the radial direction by the corresponding pressing portion 44 of the rotating cam 40 described with reference to fig. 4. Therefore, in practice, the pressed surface portion 32 of each pawl 30 is configured such that the quality control surface Q is provided in the regions on both sides in the circumferential direction where the arrangement does not coincide with the ride projection 34, and the quality control surface Q is not provided in the regions in the circumferential direction where the arrangement coincides with the ride projection 34. According to this configuration, even if the offset surface portion 30B of each pawl 30 and the riding projection 34 are arranged to coincide with each other in the circumferential direction, the quality control surface Q can be appropriately provided for each pawl 30, and molding can be performed well.

(rotating cam 40)

As shown in fig. 5, the rotary cam 40 is formed by cutting one metal plate member into a substantially disc shape and half blanking at a position in the plate thickness direction (axial direction). The above-mentioned rotating cam 40 is provided in a state of being accommodated in the cam accommodating groove 24B formed on the inner surface of the disc main body 21 of the above-mentioned guide 20.

As shown in fig. 9, the shape of the above-described rotating cam 40 has a plate thickness substantially the same as that of each of the above-described pawls 30, and the above-described rotating cam 40 is arranged to be surrounded by the main body surface portion 30A of each of the pawls 30 from the outer peripheral side in such a manner that the rotating cam 40 is sandwiched between the inner surface of the disc main body 21 of the above-described guide 20 and the offset surface portion 30B of each of the pawls 30 pushed out in a half die cut shape in the axial direction.

As shown in fig. 5, at a central portion (on the central axis C) of the above-described rotating cam 40, a through hole 41 is formed, into which the operating pin 5A integrally connected to the reclining lever 5 described with reference to fig. 1 is inserted from the inner side in the axial direction and is integrally mounted in the through hole 41 in the rotational direction. The above-described operation pin 5A is inserted through the through hole 41 of the above-described rotating cam 40 from the inside to the outside in the axial direction, and is integrally connected at that point with the reclining lever 5 described with reference to fig. 1. According to this configuration, the operating pin 5A is operated to rotate integrally with the rotating cam 40 in accordance with the above-described pull-up operation of the reclining lever 5.

The above-described operating pin 5A is integrally connected to the operating pin 5A via a connecting rod 5B, the operating pin 5A being inserted into the device 4 on the other side described with reference to fig. 1. According to this configuration, the operating pin 5A on the other side also rotates integrally, and the rotating cam 40 of the device 4 on the same side also rotates integrally by the above-described pull-up operation of the reclining lever 5.

As shown in fig. 5, the above-described rotating cam 40 is formed in a substantially disc-like shape slightly larger than the through-hole 21A formed at the central portion (on the central axis C) of the above-described guide 20, and two hook pins 43 are formed to protrude in the axial direction on the outer surface of the rotating cam 40 facing the inside of the through-hole 21A of the guide 20. As shown in fig. 2 and 6, an inner end portion 51 of a locking spring 50 described later is hooked on each of the above-described hook pins 43 in such a manner as to be sandwiched therebetween, so as to be integrally fixed. Further, on the inner surface of the above-described rotating cam 40 facing the offset surface portion 30B of each pawl 30, three pull-in pins 42 are formed to project in the axial direction, the three pull-in pins 42 being provided to be inserted into the corresponding pull-in holes 33 formed in each pawl 30, respectively.

The rotating cam 40 is assembled to the guide 20 in a state of being elastically supported via a locking spring 50. That is, from the state in which the rotating cam 40 is disposed in the cam receiving groove 24B of the above-described guide 20, the rotating cam 40 is assembled to the guide 20 in a state of being elastically supported via the locking spring 50 by disposing the locking spring 50 in the through hole 21A of the guide 20 in such a manner that the inner end portion 51 of the locking spring 50 is hooked between the hook pins 43 and the outer end portion 52 of the locking spring 50 is hung in the hanging hole 21Aa, the hook pins 43 protruding from the outer surface of the rotating cam 40 facing the inside of the through hole 21A of the guide 20, the hanging hole 21Aa extending from the through hole 21A of the guide 20.

According to such an assembly, as shown in fig. 9, the rotating cam 40 is supported in a state of being sandwiched in the axial direction between the disc main body 21 of the above-described guide 20 and the offset surface portion 30B of each of the pawls 30 (the offset surface portion 30B is pushed out in the axial direction in a half blanking shape), and the rotating cam 40 is provided so as to be surrounded from the outside in the radial direction by the pressed surface portion 32 in the radial direction, the pressed surface portion 32 being an inner peripheral surface portion of the main body surface portion 30A of each of the pawls 30.

The above-described rotating cam 40 is always in a state of being rotationally biased in the counterclockwise direction shown in fig. 10 with respect to the guide 20 by the spring biasing force of the lock spring 50 (see fig. 2 and 6), the lock spring 50 being hooked between the rotating cam 40 and the guide 20. Since being rotated in the counterclockwise direction by the bias, the rotating cam 40 is operated by each pressing portion 44 (which each pressing portion 44 is formed to protrude at a plurality of positions in the circumferential direction on the outer circumferential surface portion of the rotating cam 40) so as to push the pressed surface portion 32 of each pawl 30 from the inside to the outside in the radial direction.

Further, by the operation of pulling up the reclining lever 5 described above with reference to fig. 1, the above-mentioned rotating cam 40 is rotated in the clockwise direction shown in the drawing, which is the opposite direction to the above-mentioned biasing direction shown in fig. 11, by the operating pin 5A. As a result, the rotating cam 40 is operated to pull each pawl 30 inward in the radial direction by a shape in which each pull-in pin 42 inserted into the pull-in hole 33 of each pawl 30 moves outward in the radial direction of each pull-in hole 33 while moving in the circumferential direction in each pull-in hole 33.

Specifically, the above-described rotating cam 40 is configured such that in a state (locked state) in which each pawl 30 is pushed out from the inside in the radial direction by the rotational force caused by the spring biasing force of the locking spring 50 and meshes with the inner peripheral teeth 12A of the ratchet 10 as shown in fig. 10, the inner end portion 51 of the locking spring 50 hooked on the hook pin 43 is located in an area in the circumferential direction between two guide walls M1 on the upper left and upper right sides in the drawing among the three guide walls 23 formed on the guide 20.

In the above state, by the spring biasing force received from the inner end portion 51 of the locking spring 50, the rotating cam 40 receives the biasing force eccentrically toward the outside in the radial direction in addition to the rotational biasing force in the counterclockwise direction in the drawing. Even so, when the pawls 30 are engaged with the inner peripheral teeth 12A of the ratchet 10, the rotating cam 40 is supported by the pawls 30 and held in a centered state in the center portion (on the center axis C) of the guide 20.

However, as shown in fig. 11, in a state where the above-described rotating cam 40 is rotated in the clockwise direction shown in the drawing against the spring biasing force of the above-described locking spring 50 and each of the pawls 30 is not engaged with the inner peripheral teeth 12A of the ratchet 10, the rotating cam 40 is rotated in the clockwise direction shown in the drawing in the following manner due to the biasing action in the eccentric direction received from the inner end portion 51 of the above-described locking spring 50: as shown in fig. 16, the rotating cam 40 slides on the support surfaces 23B on the inner peripheral sides of the two guide walls M1 while being pressed against the support surfaces 23B on the inner peripheral sides of the two guide walls M1. At this time, unlike the other two guide walls M1, one remaining guide wall M2 is formed in such a manner that a slight gap T is provided between the outer circumferential surface of the above-described rotating cam 40 and the guide wall M2 in the radial direction.

According to this configuration, as shown in fig. 16, in the two guide walls M1 (the rotating cam 40 is pressed against the two guide walls M1 by the biasing force of the locking spring 50), while the rotating cam 40 is appropriately supported so as not to move in the axial displacement direction (the eccentric direction), when the shape is rocked in a certain direction of the one remaining guide wall M2 with the two guide walls M1 as a fulcrum, the rotating cam 40 appropriately disengages from the movement, so that the rotating cam 40 can smoothly slide and rotate in the release direction without eccentricity.

(peripheral ring 60)

As shown in fig. 4 and 5, the outer peripheral ring 60 is formed into a substantially cylindrical shape having a hollow disc seat by punching one thin plate material into an annular shape and drawing the outer peripheral portion of the punched hollow disc into a cylindrical shape that protrudes in the plate thickness direction (axial direction). As a result, the peripheral ring 60 has: a hollow disk-shaped flange portion 62, the flange portion 62 facing a surface in the axial direction; and a coupling portion 61 that protrudes in a substantially cylindrical shape in the axial direction along an outer peripheral edge portion of the flange portion 62.

Specifically, the above-described outer peripheral ring 60 is formed by pushing out the above-described coupling portion 61 from the outer peripheral portion of the flange portion 62 in a shape projecting in two steps in the axial direction, thereby forming the outer peripheral ring 60 into a stepped cylindrical shape having an inner and outer two-step stepped cylindrical shape in which a stepped portion 63 is formed on the inner peripheral side of the coupling portion 61, the stepped portion 63 being smaller than the coupling portion 61 in the axial direction and projecting into a substantially cylindrical shape. After the three pawls 30, the rotating cam 40, and the locking spring 50 are provided on the above-described guide 20 and the ratchet 10 are assembled together, the assembled unit is disposed inside the cylindrical interior, and the coupling portion 61 is welded to the guide 20 so that the above-described outer peripheral ring 60 is mounted on the outer peripheral portions of the ratchet 10 and the guide 20.

Specifically, the above-described unit is arranged to be first assembled from the ratchet 10 inside the cylindrical interior, so that as shown in fig. 9 and 15, the above-described outer peripheral ring 60 is arranged in such a manner that the end portion on the inner side in the radial direction of the flange portion 62 abuts on the inclined surface 13G which is inclined outward in the radial direction and is formed on the outer side surface portion in the axial direction of the intermediate cylindrical portion 13 of the ratchet 10 in substantially the entire circumferential direction. With this arrangement, the cylindrical portion 22 of the guide 20 is disposed in the cylindrical coupling portion 61 of the outer peripheral ring 60 so as to be fitted therein.

Therefore, after the above-described setting, the coupling portion 61 of the outer peripheral ring 60 is coupled to the cylindrical portion 22 of the guide 20 fitted therein by laser welding from the outer peripheral side, so that the outer peripheral ring 60 is mounted on the outer peripheral portions of the ratchet 10 and the guide 20. The inclined surface 13G formed on the outer side surface portion of the intermediate cylindrical portion 13 of the ratchet 10 described above is formed over the entire area of the ratchet 10 in the circumferential direction so as to draw a prefix tapered shape around the center portion (on the center axis C) of the ratchet 10.

By such an assembly, the peripheral ring 60 is integrally coupled to the above-described guide 20, so that the ratchet 10 is held relative to the guide 20 with the play filled in the axial direction and the radial direction by the flange portion 62. Specifically, the above-described outer peripheral ring 60 is set in a state in which the flange portion 62 of the outer peripheral ring 60 is abutted against the inclined surface 13G of the ratchet 10 in the axial direction, and the coupling portion 61 is welded and assembled to the cylindrical portion 22 of the guide 20, the guide 20 being assembled to the ratchet 10 and positioned in the axial direction. As a result, the outer peripheral ring 60 is in a state in which the ratchet 10 is loose in the axial direction between the flange portion 62 and the disc main body 21 of the guide 20, and the ratchet 10 is supported relative to the guide 20, so that the ratchet 10 can be smoothly rotationally moved without rattling in the axial direction and the radial direction when unlocked.

(conclusion)

As described above, according to the device 4, in the coupling region a4 (fourth region) of the outer side surface portion of the ratchet 10 to the seat frame 2F, the portion corresponding to the other region A3 (third region) of the protrusion 13 has the enlarged surface portion 11B, which enlarged surface portion 11B is wider outward in the radial direction than the portion corresponding to the free region a2 (second region). Therefore, the device 4 can enlarge the portion where the ratchet 10 is coupled to the seat frame 2F to the outside in the radial direction, as compared with the related-art seat reclining device.

Further, according to the device 4, it is possible to allocate, in the coupling region a4 (fourth region), a wide space in which a space around both ends of the pin 14 (protrusion) in the circumferential direction is continuous with a space outside of the pin 14 in the radial direction. Thus, the distribution ratchet 10 can be coupled to a wider area of the seat frame 2F.

(other embodiments)

The mode for carrying out the invention has been described in one embodiment, but the invention can be carried out in various modes in addition to the above-described embodiment. For example, the vehicle seat reclining device of the present invention may be applied not only to seats other than the right seat of an automobile but also to seats of vehicles other than automobiles (such as trains), and seats provided for various vehicles (such as airplanes and ships). Further, the vehicle seat reclining device described above is configured such that the seat back is connected to the seat cushion in a state in which the backrest angle is adjustable, and may also be configured such that the seat back is connected to a base fixed to the vehicle body side, such as a bracket, in a state in which the backrest angle is adjustable.

Further, the vehicle seat reclining device may be configured such that: the ratchet is coupled to a member fixed to a vehicle body side (such as a seat cushion), and the guide is coupled to a seat back. Further, the plurality of pawls forming the locking mechanism of the vehicle seat reclining device may be provided by arranging two or four or more in the circumferential direction. The arrangement of each pawl in the circumferential direction is not limited to being uniformly arranged, but may be arranged offset.

Further, the cam that operates to push each pawl outward in the radial direction may be of ｃA type that pushes each pawl outward in the radial direction by rotating, or may be of ｃA type that slides each pawl in the radial direction to push out each pawl in ｃA radial direction that intersects with the sliding direction (see JP- ｃA-2015-227071). The operation of pulling back each pawl in the radial direction inwardly may be performed by a member (e.g., a release plate) separate from the cam (see the same publication).

Furthermore, the coupling area of the seat frame abutting and coupled to the ratchet can be abutted and coupled to the seat frame without the pin.

Here, the characteristics of the embodiment of the vehicle seat reclining device 4 according to the present invention described above will be briefly summarized in [1] and [2] below.

[1]

A vehicle seat reclining device (4), comprising:

a disc-shaped ratchet (10) and a disc-shaped guide (20), the ratchet (10) and the guide (20) being coaxially assembled in a relatively rotatable manner;

a locking mechanism disposed between the ratchet (10) and the guide (20) and capable of restricting relative rotation between the ratchet (10) and the guide (20); and

a retaining ring (60), the retaining ring (60) retaining an assembled state of the ratchet (10) and the guide (20),

wherein the locking mechanism comprises: a plurality of pawls (30) supported by the guide (20) to be movable in a radial direction, the plurality of pawls (30) engaging with the ratchet (10) when moving outward in the radial direction to restrict the relative rotation between the ratchet (10) and the guide (20); and a cam (40), the cam (40) for moving the plurality of pawls (30) outwardly or inwardly in the radial direction,

wherein the ratchet (10) has: an annular protrusion (13) at which an outer peripheral portion of the ratchet (10) protrudes to one side in an axial direction; and an outer side surface portion configured to face a seat frame (2F) on the other side of the ratchet (10) in the axial direction,

wherein the protrusion (13) has: a first region (A1) in which a specific pawl (30) of the plurality of pawls (30) is allowed to move outward in the radial direction and engage with the ratchet (10); a second region (A2) in which the specific pawl (30) is prevented from moving outward in the radial direction and engaging with the ratchet (10); and a third region (A3) in which another pawl (30) is located when the specific pawl (30) is in the second region (A2), the first region (A1), the second region (A2), and the third region (A3) being arranged in the circumferential direction,

wherein the outer side surface portion has a fourth region (A4) configured to be in contact with and coupled to the seat frame (2F), and

wherein the protrusion (13) has a shape in which the third region (A3) extends further outward in the radial direction than the second region (a2), so that the fourth region (a4) has a shape in which a portion of the fourth region (a4) corresponding to the third region (A3) is wider outward in the radial direction than a portion of the fourth region (a4) corresponding to the second region (a 2).

[2]

The vehicle seat reclining device (4) according to [1],

wherein the outer side surface portion has a projection (14), the projection (14) projecting toward the other side in the axial direction so as to be fitted into the seat frame (2F), the projection (14) is provided on the fourth region (A4), and

wherein the projection (14) has a shape in which a length of the projection (14) in the circumferential direction is equal to or smaller than a length of the third region (A3) in the circumferential direction.

The present application is based on japanese patent application No. 2018-031927 filed on 26.2.2018, the contents of which are incorporated herein by reference.

INDUSTRIAL APPLICABILITY

According to the vehicle seat reclining device of the present invention, it is possible to enlarge the coupling area of the ratchet to the seat frame. The present invention having such an effect can be used for a seat of an automobile or the like, for example.

List of reference numerals

1 seat

2 seat back

2F side frame (seat frame)

2Fa Assembly hole

2Fb channel hole

3 seat cushion

3F inclination angle adjusting plate

3Fa assembly hole

3Fb passage hole

4 seat inclination angle adjusting device (vehicle seat inclination angle adjusting device)

5 Dip angle adjusting rod

5A operating pin

5B connecting rod

6 return spring

10 ratchet wheel

11 disc main body

11A through hole

11B enlarged surface portion

12 cylindrical part

12A inner peripheral teeth

13 middle cylindrical part (projection)

Region 13A

Region 13B

Region 13C

13D first projection

13E second projection

13F escape recess

13G inclined surface

A1 locking zone (first zone)

A2 free zone (second zone)

A3 other regions (third region)

A4 joining region (fourth region)

14 pin

W weld

20 guide piece

21 disc body

21A through hole

21Aa lifting hole

21B pin

21C play filler pin

22 cylindrical part

23 guide member wall

23A limiting surface

23B support surface

23C boss part

M1 guide wall

M2 guide wall

T gap

24A pawl receiving recess

24B cam receiving groove

30 ratchet pawl

30A main body surface part

30B offset surface section

31 peripheral teeth

32 is pressed on the surface

33 draw-in hole

34 ride-on projection

34A outer peripheral surface portion

34B inclined surface

35 clearance fill hole

P1 Main pawl (Special pawl)

P2 auxiliary pawl (another pawl)

Q quality control surface

40 rotating cam (cam)

41 through hole

42 draw-in pin

43 hook pin

44 extrusion part

50 locking spring

51 inner end portion

52 outer end of the tube

60 peripheral ring (retaining ring)

61 coupling part

62 flange part

63 step part

C central axis