WO2021100554A1

WO2021100554A1 - Reclining device

Info

Publication number: WO2021100554A1
Application number: PCT/JP2020/041887
Authority: WO
Inventors: 貴裕川原; 木村　明弘
Original assignee: シロキ工業株式会社
Priority date: 2019-11-18
Filing date: 2020-11-10
Publication date: 2021-05-27

Abstract

Provided is a reclining device including an adjustment mechanism and an engagement/disengagement mechanism, which can realize angle adjustment without swinging a seat back. The reclining device comprises a power-driven mechanism and a manually-driven mechanism. The power-driven mechanism includes: an internal gear having a first tooth part having a first number of teeth; and a common gear that is rotatably disposed at a position facing the internal gear and has a second tooth part having a second number of teeth different from the first number of teeth. Furthermore, the manually-driven mechanism includes: a lock member that has a lock tooth capable of locking the rotation of the common gear and can move between a lock position and an unlock position; a guide member that guides the movement operation of the lock member; and locked teeth that are fixed to the common gear and can engage with the lock tooth to form a locked state. In the common gear, the locked teeth having the same diameter and the same number as teeth of the second tooth part are arranged on the axially front and rear surfaces of the common gear.

Description

Reclining device

An embodiment of the present invention relates to a reclining device.

Conventionally, for example, a seat mounted on a vehicle (automobile or the like) is composed of a seat cushion which is a seat surface and a seat back which is a back support surface. In the case of vehicle seats, a so-called reclining device that can adjust the posture of the seat according to the physique and preferences of the user (for example, passengers, etc.), usage conditions, etc., that is, the inclination angle of the seat back with respect to the seat cushion. Is often built-in. For example, when driving a vehicle, the angle can be finely adjusted in order to realize a seat back angle that does not cause fatigue. In this case, for example, there is a device in which the angle is adjusted by using the power from a power source such as a motor. On the other hand, there are cases where it is desired to adjust the tilt angle of the seat back significantly and quickly. For example, when it is desired to adjust the seat back to an angle close to flat for a break or the like, or when, for example, when getting on and off the rear seat in a two-door type vehicle, the seat back is greatly tilted forward. In this case, the angle of the seat back can be adjusted by releasing the lock mechanism (engagement / disengagement mechanism) of the seat back with respect to the seat cushion by operating an operation lever or the like.

Japanese Patent No. 4189760

In the case of the structure of the prior art, the planetary gear mechanism is composed of the first gear provided on the seat cushion side and the second gear provided on the seat back side, and the reduction ratio is increased to lock by the engagement / disengagement mechanism. In the state, the angle of the seat back with respect to the seat cushion can be finely adjusted. However, because it uses a planetary gear mechanism, when adjusting the angle of the seat back, the seat back rotates (swings) while being eccentric, which makes the user seated in the seat feel uncomfortable. There was a problem that it was easy to give.

Therefore, one of the problems of the present invention is to obtain a reclining device provided with an adjustment mechanism and an engagement / disengagement mechanism that can realize angle adjustment without swinging the seat back.

The reclining device according to the embodiment of the present invention is, for example, a power drive mechanism that executes the angle adjustment of the seat back with respect to the seat cushion by power from the drive source, and a lock for manually operating the angle adjustment of the seat back. It is equipped with a manual drive mechanism for releasing. The power drive mechanism includes an internal gear having a first tooth portion having a first number of teeth and a second tooth different from the first number of teeth, which is rotatably arranged at a position facing the internal gear. Includes a common gear with a number of second teeth. Further, the manual drive mechanism has lock teeth that can lock the rotation of the common gear, a lock member that can move between the lock position and the unlock position, and a guide that guides the movement operation of the lock member. Includes a member and locked teeth that are fixed to the common gear and can mesh with the lock teeth to form a locked state. Then, in the common gear, the locked teeth having the same diameter and the same number of teeth as the second tooth portion are arranged on the front and back surfaces with respect to the axial direction of the common gear. According to this configuration, for example, by extruding the second tooth portion with respect to the plate material by, for example, pressing, it becomes possible to form locked teeth on the back surface side of the plate material. As a result, the second tooth portion having the same diameter and the locked tooth can be arranged on the common gear, which can contribute to the miniaturization of the common gear (avoidance of increasing the diameter of the common gear) and, by extension, the miniaturization of the reclining device. In addition, gears for different purposes can be efficiently formed, which can contribute to cost reduction.

Further, the manual drive mechanism of the reclining device according to the embodiment of the present invention is rotatably supported by, for example, a bracket that supports the guide member and the bracket that is concentric with the rotation center of the common gear. A ring-shaped cam member for moving the lock member between the lock position and the unlock position is provided, and the lock member moves based on the rotational posture of the cam member to reach the lock position. , The unlocked position may be reachable. According to this configuration, for example, the lock member can be stably moved based on the rotational posture of the cam member supported by the bracket, so that the locked state and the unlocked state can be switched smoothly and stably. can do.

Further, the bracket of the reclining device according to the embodiment of the present invention includes, for example, a ring-shaped accommodating portion on the outer peripheral side of the guide member, and the cam member is a ring supported on the inner peripheral side of the accommodating portion. The lock member may move in the inner diameter direction to reach the lock position on the inner peripheral side of the cam member, and may move in the outer diameter direction to reach the unlock position. .. According to this configuration, for example, the lock member can be stably moved in the radial direction on the inner peripheral side of the cam member supported by the bracket without being eccentric, so that the locked state and the unlocked state can be switched. Can be realized smoothly and stably.

FIG. 1 is an exemplary and schematic side view showing a vehicle seat to which the reclining device according to the embodiment can be applied. FIG. 2 is an exemplary and schematic exploded perspective view of the reclining device according to the embodiment, and is a view when the viewpoint is placed on the manual drive mechanism side. FIG. 3 is an exemplary and schematic exploded perspective view of the reclining device according to the embodiment, and is a view when the viewpoint is placed on the power drive mechanism side opposite to the viewpoint of FIG. FIG. 4 is an exemplary and schematic cross-sectional view of the reclining device according to the embodiment. FIG. 5 is an exemplary and schematic diagram illustrating the meshing state of the gears of the power drive mechanism in the reclining device according to the embodiment. FIG. 6 is an exemplary and schematic view illustrating the meshing state of the lock member and the gear of the manual drive mechanism in the reclining device according to the embodiment. FIG. 7 is an exemplary and schematic diagram illustrating a locked state of the manual drive mechanism in the reclining device according to the embodiment. FIG. 8 is an exemplary and schematic diagram illustrating an unlocked state of the manual drive mechanism in the reclining device according to the embodiment.

Hereinafter, exemplary embodiments of the present invention will be disclosed. The configurations of the embodiments shown below, as well as the actions, results, and effects produced by the configurations, are examples. The present invention can be realized by a configuration other than the configurations disclosed in the following embodiments, and at least one of various effects based on the basic configuration and derivative effects can be obtained. ..

FIG. 1 is an exemplary and schematic side view showing a vehicle seat 100 to which the reclining device according to the embodiment can be applied. As shown in FIG. 1, the seat 100 is connected to a seat cushion 102, which is a seating surface on which a user (passenger) sits, with an adjustable angle in the direction of arrow A1 or arrow A2 with respect to the seat cushion 102. It is composed of a seat back 104 that serves as a back support surface. The seat cushion 102 is fixed to a seat slider device 110 that can move in the direction of arrow B1 or arrow B2 on a rail 108 fixed to the floor 106, which is the floor surface of the vehicle. The angle of the seat back 104 can be adjusted with respect to the seat cushion 102 with the rotating shaft 112 extending in the vehicle width direction as a fulcrum via the reclining device 10 of the present embodiment. The reclining device 10 is arranged inside the seat 100, for example, coaxially with the rotation shaft 112.

The amount of movement of the seat cushion 102 in the arrow B1 direction or arrow B2 direction and the amount of angle adjustment of the seat back 104 in the arrow A1 direction or arrow A2 direction are determined by, for example, a drive source such as a motor that is driven according to the operating state of the adjustment switch SW. It can be adjusted by power. For example, by sliding the adjustment switch SW in the direction of arrow B1, the seat cushion 102 can be moved to a preset position or a desired position in the direction of arrow B1. Similarly, by sliding the adjustment switch SW in the direction of arrow B2, the seat cushion 102 can be moved to a preset position or a desired position in the direction of arrow B2. Further, by unlocking the slide lever LS, the locked state of the seat cushion 102 is released, and the seat cushion 102 can be appropriately moved to the position in the B1 direction or the B2 direction. After the seat cushion 102 is moved, the seat cushion 102 can be fixed at a desired position by locking the slide lever LS.

Further, by rotating the adjustment switch SW in the direction of arrow A1, the reclining device 10 operates, and the seat back 104 can be adjusted to a preset angle or a desired angle in the direction of arrow A1. Similarly, by rotating the adjustment switch SW in the direction of arrow A2, the reclining device 10 operates, and the seat back 104 can be adjusted to a preset angle or a desired angle in the direction of arrow A2. Further, by rotating the reclining lock release lever LR in a predetermined direction, the reclining lock of the reclining device 10 can be released, and the seat back 104 can be reclining at a desired angle with respect to the seat cushion 102. The configuration of the adjustment switch SW is an example, and the automatic slide adjustment of the seat cushion 102 and the automatic reclining adjustment of the seat back 104 may be performed by separate switches. The arrangement of the adjustment switch SW can be changed as appropriate, and may be provided on the dashboard, steering wheel, or the like, for example. Note that FIG. 1 shows, for example, the passenger seat of a right-hand drive vehicle. In the seat on the driver's seat side, the adjustment switch SW, the reclining lock release lever LR, and the like may be arranged on the opposite side of the seat 100.

2 and 3 are exploded perspective views of the reclining device 10 of the present embodiment, FIG. 2 is a view when viewed from the arrow L direction, and FIG. 3 is a view when viewed from the arrow R direction. .. Further, FIG. 4 is a cross-sectional view of the reclining device 10 in an assembled state.

The reclining device 10 includes a power drive mechanism D (sometimes referred to as a power drive mechanism or an adjustment mechanism) that executes angle adjustment of the seat back 104 with respect to the seat cushion 102 by power from a drive source (for example, an electric motor), and a seat. It is composed of a manual drive mechanism M (sometimes referred to as a manual drive mechanism or an engagement / disengagement mechanism) that releases the reclining lock in order to enable manual operation of the angle adjustment of the back 104.

The power drive mechanism D includes a common gear 12, a first bush 14, a striker pin 16, a wedge spring 18, a wedge 20, an eccentric cam plate 22, an external gear 24, an internal gear 26, a second bush 28, an outer ring 30, and the like. It is composed of.

Further, the manual drive mechanism M includes a common gear 12 shared with the power drive mechanism D, a lock member 32 (sometimes referred to as a pole), a cam ring 34 (cam member), a cam plate 36, a lower arm 38 (bracket), and a lock spring. It is composed of 40 mag.

In the reclining device 10, the common gear 12, the first bush 14, the striker pin 16, the wedge spring 18, the wedge 20, the eccentric cam plate 22, the external gear 24, the internal gear 26, the second bush 28 and the lock member 32, and the cam ring. 34. The cam plate 36 is maintained in an assembled state while being sandwiched between the outer peripheral ring 30 and the lower arm 38. The outer peripheral ring 30 is provided with an opening hole 30a so that the end face of the internal gear 26 is exposed so that the outer ring 30 can be connected to a seat back frame or the like that supports the seat back 104. Further, the lower arm 38 is fixed to a cushion frame (not shown), a floor 106, or a rail 108 that constitutes the seat cushion 102. That is, it is fixed to the vehicle side.

First, the power drive mechanism D will be described in detail of the reclining device 10 configured as described above.

As shown in FIGS. 2 to 4, the common gear 12 is, for example, a disk-shaped member (steel plate or the like) having a plate-like member (steel plate or the like) pressed or cut to form a plurality of step portions to improve the strength. It is a member. Further, as shown in FIG. 3, in the common gear 12, for example, a through hole 12c is formed in a portion corresponding to the rotation center axis O by punching, and the common gear 12 is recessed toward the power drive mechanism D side by press working. A bottom portion 12a and a side surface portion 12b are formed. At this time, by using a gear-shaped press mold, internal teeth (second internal teeth 42) can be formed on the side surface portion 12b (recessed inner peripheral surface). At the same time, protruding external teeth (second external teeth 44) are formed on the manual drive mechanism M side of the common gear 12 extruded by the gear-shaped press mold as shown in FIG. In this case, the second internal tooth 42 and the second external tooth 44 have the same diameter and the same rotation center axis O, and are molded and arranged on the front and back surfaces in the axial direction. As a result, the second internal tooth 42 and the second external tooth 44 can be formed on the common gear 12 at the same time, which can contribute to simplification, efficiency, and cost reduction of the manufacturing process. Further, by arranging the second internal tooth 42 and the second external tooth 44 on the front and back of the common gear 12, it is possible to save space when arranging a plurality of gears, and the common gear 12 can be downsized (small diameter). ) Is possible. In another embodiment, in the common gear 12, the diameter of the second internal tooth 42 and the diameter of the second external tooth 44 may be different. In the common gear 12 configured as described above, the external teeth (first external teeth 46) of the external tooth gear 24 are engaged with the second internal teeth 42, and the lock member 32 is locked with the second external teeth 44. The teeth (third internal tooth 48) mesh. The meshing of each gear will be described later.

The internal gear 26 is also a disk-shaped member with improved strength, in which a plate-shaped member (for example, a steel plate) is pressed or cut to form a step portion. As shown in FIG. 2, in the internal gear 26, for example, a through hole 26c is formed in a portion corresponding to the rotation center axis O by punching, and a common gear 12 (manual drive mechanism M) is formed by pressing. ) Side recessed bottom portion 26a and side surface portion 26b are formed. At this time, by using a gear-shaped press mold, internal teeth (first internal teeth 50) can be formed on the side surface portion 26b (recessed inner peripheral surface). In the internal gear 26, a plurality of (for example, three) fastening members 26d (for example, protrusions punched from the bottom 26a side) protrude on the surface on the back side of the surface on which the first internal tooth 50 is formed. There is. By inserting and welding the fastening member 26d into a hole formed in the seat back frame or the like that supports the seat back 104, the seat back 104 can be fixed to the internal gear 26 (reclining device 10). When the first internal tooth 50 is formed by a gear-shaped press die, a protruding gear-shaped protrusion 52 is formed on the back surface as shown in FIG. The gear-shaped protrusion 52 can be used as a spline, and may be meshed with a spline groove formed in a seat back frame or the like. In this case, the seat back 104 can be more firmly fixed to the internal gear 26.

As shown in FIG. 4, the external gear 24 meshes with the second internal tooth 42 of the common gear 12 and has a first external tooth 46 that can mesh with the first internal tooth 50 of the internal gear 26 on the outer peripheral surface. It is a ring-shaped member provided with an opening 24a. In this case, in the first external tooth 46, for example, half of the tooth width meshes with the second internal tooth 42 of the common gear 12, and the other half region meshes with the first internal tooth 50 of the internal gear 26. It is configured as follows. In the case of the present embodiment, the number of teeth of the second internal tooth 42 of the common gear 12 and the number of teeth of the first internal tooth 50 of the internal gear 26 are different. For example, the second internal tooth 42 of the common gear 12 is set to have a smaller number of teeth than the first internal tooth 50 of the internal gear 26. The first external teeth 46 of the external gear 24 are set to have a smaller number of teeth than the second internal teeth 42 of the common gear 12. For example, the first internal tooth 50 of the internal gear 26 is set to 27, the second internal tooth 42 of the common gear 12 is set to 26, and the first external tooth 46 of the external gear 24 is set to 23. Therefore, as shown in FIG. 5, when the external gear 24 is combined so as to mesh with the common gear 12 and the internal gear 26, the external gear 24 with respect to the common gear 12 and the internal gear 26. It will rotate eccentrically. Due to this eccentric rotation, the first external tooth 46 of the external gear 24 repeatedly meshes with and disengages from the second internal tooth 42 of the common gear 12 and the first internal tooth 50 of the internal gear 26. .. As described above, since the number of teeth of the second internal tooth 42 in the common gear 12 is set to be one less than the number of teeth of the first internal tooth 50 of the internal gear 26, the external gear 24 makes one rotation. Each time, the internal gear 26 rotates in the same direction as the external gear 24 by one tooth with respect to the common gear 12 (the common gear 12 is non-rotating). That is, it is possible to finely adjust the inclination angle of the seat back 104 connected to the internal gear 26 while decelerating the rotation of the motor (rotation of the drive shaft DS) input to the internal gear 26. In the above example, the difference in the number of teeth between the second internal tooth 42 and the first internal tooth 50 is different by "1", but the difference in the number of teeth may be 2 or more, depending on the angle adjustment speed to be realized. Can be changed as appropriate.

A disk-shaped eccentric cam plate 22 is fitted into the opening 24a formed in the external gear 24. An opening 22a eccentric from the rotation center axis O is formed in the eccentric cam plate 22, and a striker pin 16, a wedge spring 18, and two wedges 20 (20a, 20b) are housed therein. The striker pin 16 is a tubular member having a flange around it. One end of the tubular portion is inserted into the through hole 12c of the common gear 12 via the first bush 14, and the other end is a through hole of the internal gear 26. It is inserted into the 26c via the second bush 28 and is supported so that it can rotate smoothly and stably. The tubular portion of the striker pin 16 constitutes a bearing portion 16a extending along the rotation center axis O, and a spline or the like is formed on the inner peripheral surface of the bearing portion 16a. As shown in FIG. 4, a drive shaft DS of a drive source such as a motor that automatically performs reclining adjustment is inserted into the bearing portion 16a and fixed by spline fitting. Further, two protrusions 16b (16ba, 16bb) are formed on a part of the flange on the outer peripheral surface of the striker pin 16, and the protrusions 16b are configured to abut on one end of the arc-shaped wedge 20. .. For example, as shown in FIG. 5, when the drive shaft DS is driven in the forward direction (driven in the clockwise direction) to adjust the reclining angle of the seat back 104, the protrusion 16ba pushes one end side of the wedge 20a, and further. The other end of the wedge 20a pushes the protrusion 22b formed in a part of the opening 22a of the eccentric cam plate 22. That is, the external gear 24 can be eccentrically rotated in the forward rotation direction by the forward rotation drive of the drive shaft DS. Similarly, when the drive shaft DS is driven in reverse direction (driven in the counterclockwise direction) in order to adjust the reclining angle of the seat back 104, the protrusion 16bb pushes one end side of the wedge 20b, and the other end side of the wedge 20b is eccentric. Push the protrusion 22b of the cam plate 22. That is, the external gear 24 can be eccentrically rotated in the reverse direction by the reverse drive of the drive shaft DS. The substantially C-shaped wedge spring 18 shown in FIG. 2 urges the ends of the wedges 20 (20a, 20b) in the separation direction (circumferential direction) inside the opening 22a of the eccentric cam plate 22. This prevents the wedge 20 from rattling (vibrating) inside the opening 22a.

As described above, according to the power drive mechanism D of the present embodiment, each time the eccentric rotating external gear 24 makes one rotation, the internal gear 26 is combined with the external gear 24 by one tooth with respect to the common gear 12. Rotate in the same direction. That is, the angle of the seat back 104 connected to the internal gear 26 can be finely adjusted. In this case, only the internal gear 26 rotates eccentrically with respect to the external gear 24, and the internal gear 26 rotates about the rotation center axis O with respect to the common gear 12. Therefore, when the angle of the seat back 104 is adjusted by using the power drive mechanism D, it is possible to prevent the seat back 104 from swinging due to the eccentric movement, and it is possible to prevent the user from feeling uncomfortable.

Next, the manual drive mechanism M will be described with reference to FIGS. 2 to 4 and 6 to 8. FIG. 6 is an exemplary and schematic view illustrating the meshing state of the third internal tooth 48 of the lock member 32 of the manual drive mechanism M and the second external tooth 44 of the common gear 12, and in FIG. 3, the arrow R It is an assembly drawing seen from the direction. Further, FIG. 7 is an exemplary and schematic view for explaining the locked state Rst of the manual drive mechanism M, and the upper row is a view of the lock member 32 and the like seen through the cam plate 36 from the direction of arrow L, and the lower row is a lower row. Is a diagram in which the cam plate 36 is removed to expose the relationship between the cam ring 34 and the lock member 32. Similarly, FIG. 8 is an exemplary and schematic view illustrating the unlocked state NRst of the manual drive mechanism, and the upper row is a view of the lock member 32 and the like seen through the cam plate 36 from the direction of arrow L. The lower part is a diagram in which the cam plate 36 is removed to expose the relationship between the cam ring 34 and the lock member 32.

The manual drive mechanism M unlocks the seat back 104 with respect to the seat cushion 102 so that the seat back 104 can freely tilt with respect to the seat cushion 102 when the angle of the seat back 104 is manually adjusted. It is a mechanism to make. Further, the manual drive mechanism M is a mechanism for locking the seat back 104 when the power drive mechanism D automatically adjusts the angle of the seat back 104 and when the adjustment angle state of the seat back 104 with respect to the seat cushion 102 is maintained.

In the case of the present embodiment, when the second internal tooth 42 is formed on the common gear 12, the second external tooth 44 formed on the back surface side (manual drive mechanism M side) and the third internal tooth 48 of the lock member 32 are meshed with each other. A locked state is formed by letting the teeth engage, and an unlocked state is formed by disengaging them.

As shown in FIGS. 2, 3, 6, 6 and the like, the lock member 32 is a block-shaped member having a substantially rectangular parallelepiped shape, and is radially attached to and detached from the second outer tooth 44 on the outer peripheral side of the common gear 12. Possible, for example, are evenly spaced. In the case of the present embodiment, four lock members 32 are arranged at 90 ° intervals, but the number of lock members 32 can be appropriately changed as long as the strength that can maintain the locked state of the seat back 104 with respect to the seat cushion 102 can be secured. It may be 3 or less, or 5 or more.

As shown in FIG. 6, the lock member 32 has a curved surface corresponding to the pitch circle of the second external teeth 44 of the common gear 12, and can mesh with the second external teeth 44 along the curved surface, for example, 3. A third internal tooth 48 composed of one tooth is formed. The number of teeth of the third internal tooth 48 can be appropriately changed as long as the meshing strength capable of maintaining the locked state of the seat back 104 with respect to the seat cushion 102 can be secured.

Further, the lock member 32 is provided with leg portions 32a on the left and right sides of the third internal tooth 48, and the outer surface of the leg portion 32a is guided by a pair of guide members 38a formed on the lower arm 38. Is forming. As shown in FIG. 3, the plate-shaped lower arm 38 can be formed into a protruding guide member 38a by press working or cutting. The guide member 38a restricts the movement of the lock member 32 in the circumferential direction and allows the lock member 32 to move only in the radial direction.

In this embodiment, an example is shown in which one lock member 32 is sandwiched between a pair of guide members 38a to guide the lock member 32. However, if the lock member 32 can smoothly move in the radial direction of the second outer tooth 44, the guide member The form can be changed as appropriate. For example, one guide member may guide the lock member 32.

Further, as shown in FIG. 6, when the lock member 32 is arranged along the outer circumference of the second outer tooth 44, the leg portion on the side opposite to the forming surface of the third inner tooth 48 (outer in the radial direction). The 32a is formed with a sliding surface 32c that comes into contact with the cam portion 34a formed on the inner peripheral side of the cam ring 34. In the case of the present embodiment, as shown in FIG. 6, the cam ring 34 has four cam portions 34a corresponding to the four lock members 32 arranged at equal intervals on the outer peripheral side of the second outer tooth 44. To be equipped with. The cam portion 34a is, for example, a semicircular protrusion protruding inward in the radial direction, and is formed on the end surface of one of the leg portions 32a of the lock member 32 so as to be in contact with the sliding surface 32c. Has been done. In the case of the present embodiment, the cam portion 34a of the cam ring 34 is formed so as to abut on one of the two leg portions 32a of the lock member 32. In another embodiment, the sliding surface 32c may be formed on both leg portions 32a of the lock member 32, and the cam ring 34 may be configured so that the cam portion 34a abuts on both of them.

Further, when the lock member 32 is arranged along the outer circumference of the second outer tooth 44, a dowel 32d is formed on the lower arm 38 side in the axial direction of the rotation center axis O of the lock member 32. As shown in FIG. 2, the dowel 32d is inserted into a cam groove 36a formed in a disc-shaped cam plate 36 arranged between the cam ring 34 and the lower arm 38. As shown in the upper part of FIG. 7 and the upper part of FIG. 8, the cam groove 36a of the cam plate 36 communicates with the circumferential groove 36a1 extending in the substantially circumferential direction of the cam plate 36 and the circumferential groove 36a1 and has a substantially diameter. It is composed of an inclined groove 36a2 extending outward in the direction. The circumferential groove 36a1 is a position (lock position) in which when the dowel 32d moves from the inclined groove 36a2 to the circumferential groove 36a1, the lock member 32 engages the third inner tooth 48 and the second outer tooth 44 by the cam ring 34 described above. ) Is formed so that it can be reached. Further, in the inclined groove 36a2, the dowel 32d is guided from the circumferential groove 36a1 to the inclined groove 36a2 to reach the outer peripheral side end portion, so that the lock member 32 is not meshed with the third inner tooth 48 and the second outer tooth 44. It is formed so as to reach the position (locking / unlocking position).

As shown in the lower part of FIG. 7 and the lower part of FIG. 8, a plurality of (for example, four) dowels 34b are provided on the cam ring 34 in the circumferential direction at equal intervals, for example, on the cam plate 36 side in the axial direction of the rotation center axis O. Is formed in. On the other hand, as shown in the upper part of FIGS. 2 and 7 and the upper part of FIG. 8, a plurality of (for example, 4) positioning holes 36b are formed in the cam plate 36 at positions corresponding to the dowels 34b. Then, by inserting the dowel 34b into the positioning hole 36b, the positional relationship between the cam portion 34a and the cam groove 36a that enables the movement of the lock member 32 as described above is determined, and the cam ring 34 and the cam plate 36 are separated. It is integrated. The cam ring 34 and the cam plate 36 may be formed as an integral part in advance. The cam ring 34 integrated with the cam plate 36 surrounds the outer peripheral surface of the guide member 38a on the forming surface side of the guide member 38a centering on the through hole 38b formed at the position where the rotation center axis O passes. The ring-shaped storage portion 38c formed so as to project is rotatably supported concentrically with the rotation center axis O. As a result, the cam ring 34 (cam plate 36) can smoothly and stably rotate (slide) with respect to the lower arm 38 without being eccentric. As a result, the lock member 32, which is moved in the radial direction by the cam ring 34 (cam plate 36), also moves smoothly and stably inside (inner peripheral side) in the radial direction of the cam ring 34 (cam plate 36) to the lock position. Will be reachable. Similarly, the lock member 32 can move in the outer diameter direction to reach the unlocked position. Further, by moving the lock member 32 in the inner diameter direction to establish the locked state, the second outer tooth 44 formed on the back surface side of the common gear 12 by forming the second inner tooth 42 can be used for locking. It can be used as a gear.

The cam plate 36 is formed with a bearing portion 36c into which the operation shaft MS (see FIG. 4) of the reclining lock release lever LR (see FIG. 1) is inserted at a position where the rotation center axis O passes. The bearing portion 36c penetrates the through hole 38b provided in the lower arm 38 to expose the tip portion to the front side of the lower arm 38. A spline groove or the like is formed on the inner peripheral surface of the bearing portion 36c, and by fixing the operation shaft MS by spline fitting, the cam plate 36 and the integrated cam ring 34 can be moved by the operating force of the reclining lock release lever LR. Can be rotated. In the cam plate 36, a relief hole 36d for escaping the guide member 38a when the cam plate 36 is assembled to the lower arm 38 is formed corresponding to the position of the guide member 38a. In the case of FIG. 7, eight escape holes 36d are formed corresponding to the number of guide members 38a. The width of the relief hole 36d in the circumferential direction may be set wider than the rotation width of the cam ring 34 (cam plate 36). For example, the width corresponding to the distance between the rotation position of the cam ring 34 (cam plate 36) in which the dowel 32d is located at the end of the circumferential groove 36a1 and the rotation position when the dowel 32d is located at the end of the inclined groove 36a2. It may be set wider. In the upper part of FIG. 7, the partition between the two escape holes 36d existing between the adjacent cam grooves 36a may be omitted to form a large escape hole (four large escape holes as a whole).

The lock spring 40 is, for example, a spiral spring that constantly urges the cam plate 36 together with the cam ring 34 in the counterclockwise direction in FIG. 7. When the operating force of the reclining lock release lever LR is not applied by the urging force of the lock spring 40, the cam plate 36 and the cam ring 34 integrated with the cam plate 36 are always urged in the counterclockwise direction. As a result, the lock member 32 is moved (urged) inward in the radial direction to maintain the meshed state of the third internal tooth 48 and the second external tooth 44, that is, the locked state.

When the lock member 32 is unlocked from the cam ring 34, that is, when the third internal tooth 48 is disengaged from the second outer tooth 44 and moves outward in the radial direction, the leg portion 32a of the lock member 32 A notch portion 34c is provided adjacent to the cam portion 34a. By providing the notch portion 34c, the lock member 32 can be sufficiently moved to the unlocked position on the outer side in the radial direction, and the second outer tooth 44 and the third inner tooth 48 are caught during the unlocking operation. Etc. can be avoided.

The operation of the reclining device 10 configured in this way will be described.

First, a case where the seat back 104 is driven by a motor to adjust the angle of the seat cushion 102 by using the power drive mechanism D will be described. In this case, for example, the user seated on the seat 100 slides the adjustment switch SW shown in FIG. 1 in a desired direction in order to specify the driving direction (rotation direction) of the reclining motor. For example, when it is desired to raise the angle of the seat back 104 forward, the adjustment switch SW is slid to the arrow B1. On the contrary, when the angle of the seat back 104 is to be laid backward, the adjustment switch SW is slid to the arrow B2. While the adjustment switch SW is being slid, the drive shaft DS of the motor is rotationally driven to operate the power drive mechanism D, and the angle of the seat back 104 can be adjusted. When the hand is released from the adjustment switch SW, the adjustment switch SW returns to the neutral position and the rotation of the motor is stopped. In this case, since the reclining lock release lever LR is not operated, the cam ring 34 and the cam plate 36 are rotated in the lock direction by the urging force of the lock spring 40. That is, the lock member 32 is moved to the lock position. Therefore, the third internal tooth 48 of the lock member 32 and the second external tooth 44 of the common gear 12 mesh with each other, and the common gear 12 is fixed to the lower arm 38. Further, since the second internal tooth 42 of the common gear 12 and the first internal tooth 50 of the internal gear 26 are always meshed with each other via the first external tooth 46 of the external gear 24, the seat back with respect to the seat cushion 102. The angle of 104 can be adjusted only by the rotation of the striker pin 16, that is, by driving the reclining motor.

When the drive shaft DS of the reclining motor is rotated by the operation of the adjustment switch SW, the common gear 12 (in this case, the common gear 12 is not rotated in the locked state by the lock member 32) and the internal gear 26 as described above. On the other hand, only the external gear 24 rotates eccentrically, and the internal gear 26 to which the seat back 104 is connected rotates around the rotation center axis O without being eccentric with respect to the common gear 12. As a result, each time the external gear 24 rotates once, the internal gear 26 rotates in the same direction as the external gear 24 by one tooth with respect to the common gear 12. That is, the angle of the seat back 104 connected to the internal gear 26 can be finely adjusted. Therefore, when the angle of the seat back 104 is adjusted by using the power drive mechanism D, it is possible to prevent the seat back 104 from swinging due to the eccentric movement, and it is possible to prevent the user from feeling uncomfortable. The user can stop the angle adjustment of the seat back 104 by stopping the operation of the adjustment switch SW when the seat back 104 reaches a desired adjustment angle. As described above, since the internal gear 26 to which the seat back 104 is connected rotates for one rotation of the external gear 24, the angle of the seat back 104 can be adjusted almost at the same time as the operation of the adjustment switch SW is stopped. When stopped, the seat back 104 is fixed at the adjustment angle. The same applies to the case where the rotation direction of the drive shaft DS is switched to adjust the angle of the seat back 104 in the opposite direction.

Next, a case where the angle adjustment of the seat back 104 with respect to the seat cushion 102 is manually performed by using the manual drive mechanism M will be described.

As described above, when the reclining lock release lever LR is not operated, the cam ring 34 and the cam plate 36 rotate in the locking direction (counterclockwise in FIGS. 7 and 8) due to the urging force of the lock spring 40 to lock. The member 32 is moved to the lock position. As a result, as shown in the lower part of FIG. 7, the third internal tooth 48 of the lock member 32 and the second external tooth 44 of the common gear 12 mesh with each other, and the common gear 12 is fixed to the lower arm 38. It is in a non-rotating state. Further, since the second internal tooth 42 of the common gear 12 and the first internal tooth 50 of the internal gear 26 are always meshed with each other via the first external tooth 46 of the external gear 24, the seat back with respect to the seat cushion 102. The angle of 104 is maintained in a fixed state.

Next, when it is desired to manually change the inclination angle of the seat back 104 with respect to the seat cushion 102, the lock spring 40 is attached in a state where the leaning load on the seat back 104 is eliminated (such as when the back or hand is released from the seat back 104). The reclining lock release lever LR is rotated in a predetermined direction (in the case of FIG. 7, in the clockwise direction) against the force. As a result, the cam plate 36 and the cam ring 34 integrated with the operation shaft MS rotate, and the cam portion 34a of the cam ring 34 that is in contact with the cam plate 36 is disengaged from the sliding surface 32c of the lock member 32, and the dowel 32d of the lock member 32 is released. Is guided to the inclined groove 36a2 along the cam groove 36a of the cam plate 36. That is, the lock member 32 is pulled outward in the radial direction, and as shown in the lower part of FIG. 8, the engagement between the second outer tooth 44 of the common gear 12 and the third inner tooth 48 of the lock member 32 is released. It will be unlocked. As a result, the common gear 12 is released from the lower arm 38 connected to the seat cushion 102 side, and the entire power drive mechanism D side together with the common gear 12 becomes freely rotatable about the rotation center axis O. That is, the seat back 104 connected to the internal gear 26 can freely adjust the angle with respect to the seat cushion 102.

For example, since the seat back 104 may be urged by an urging member (spring or the like) so as to fall forward in the unlocked state, the seat back 104 is moved forward at the same time as the operation of the reclining lock release lever LR. It tilts greatly. Further, the seat back 104 can be tilted backward by pushing the seat back 104 backward with a hand or the back in the unlocked state.

If the reclining lock release lever LR is released with the seat back 104 tilted with the hand or back, the cam plate 36, the cam ring 34, and the reclining lock release lever LR rotate counterclockwise, for example, due to the urging force of the lock spring 40. .. As a result, the cam portion 34a of the cam ring 34 pushes down the sliding surface 32c of the lock member 32 inward in the radial direction, and the dowel 32d of the lock member 32 is guided to the circumferential groove 36a1 along the cam groove 36a of the cam plate 36. Then, the mode shown in the lower part of FIG. 8 is restored to the state shown in the lower part of FIG. That is, the second outer tooth 44 of the common gear 12 and the third inner tooth 48 of the lock member 32 mesh with each other to form a locked state, and the seat back 104 is fixed to the seat cushion 102 at a desired angle.

As described above, according to the present embodiment, a reclining device including a power drive mechanism D (adjustment mechanism) and a manual drive mechanism M (engagement / disengagement mechanism) that can realize angle adjustment without swinging the seat back 104 is realized. can do.

Although the reclining device 10 applied to the reclining seat for a vehicle is shown in the above-described embodiment, the reclining device 10 is not limited to the seat for a vehicle. For example, the reclining device 10 of the present embodiment can be applied to any seat that can be reclined by using the power of a drive source, such as a seat for an airplane, a seat for a ship, and a seat used in various attractions. A similar effect can be obtained.

Although the embodiments and modifications of the present invention have been described, these embodiments and modifications are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

This international application is a Japanese patent application filed on November 18, 2019, Japanese Patent Application No. 2019-208275, and a Japanese patent application filed on October 9, 2020, Japanese Patent Application No. 2020-171350. The entire contents of Japanese Patent Application No. 2019-208275 and Japanese Patent Application No. 2020-171350, which are Japanese patent applications, are incorporated in this international application.

10 ... Reclining device, 12 ... Common gear, 16 ... Striker pin, 18 ... Wedge spring, 20 ... Wedge, 22 ... Eccentric cam plate, 24 ... External gear, 26 ... Internal gear, 30 ... Outer ring, 32 ... Lock Member, 32d ... Dove, 34 ... Cam ring (cam member), 34a ... Cam part, 36 ... Cam plate, 36a ... Cam groove, 36a1 ... Circumferential groove, 36a2 ... Inclined groove, 38 ... Lower arm (bracket), 40 ... Lock Spring, 42 ... 2nd internal tooth, 44 ... 2nd external tooth, 46 ... 1st external tooth, 48 ... 3rd internal tooth (lock tooth), 50 ... 1st internal tooth, 100 ... seat, 102 ... seat cushion, 104 ... Seat back, D ... Power drive mechanism (power drive mechanism), M ... Manual drive mechanism (manual drive mechanism).

Claims

It is equipped with a power drive mechanism that adjusts the angle of the seat back with respect to the seat cushion by power from the drive source, and a manual drive mechanism that unlocks the seat back so that the angle adjustment can be manually operated.
The power drive mechanism is
An internal gear having a first tooth portion with a first number of teeth,
A common gear having a second tooth portion having a second number of teeth different from the first number of teeth, which is rotatably arranged at a position facing the internal gear.
Including
The manual drive mechanism
A locking member having a locking tooth that can lock the rotation of the common gear and being movable between a locking position and an unlocking position,
A guide member that guides the moving operation of the lock member and
Includes locked teeth that are fixed to the common gear and can mesh with the lock teeth to form a locked state.
The common gear is a reclining device in which the locked teeth having the same diameter and the same number of teeth as the second tooth portion are arranged on the front and back surfaces in the axial direction of the common gear.
The manual drive mechanism
A bracket that supports the guide member and
A cam member that moves the lock member between the lock position and the unlock position, which is rotatably supported by the bracket concentrically with the rotation center of the common gear.
With
The reclining device according to claim 1, wherein the lock member moves based on the rotational posture of the cam member to reach the lock position and the unlock position.
The bracket is provided with a ring-shaped storage portion on the outer peripheral side of the guide member.
The cam member has a ring shape supported on the inner peripheral side of the storage portion.
The lock member can move in the inner diameter direction to reach the lock position and can move in the outer diameter direction to reach the unlock position on the inner peripheral side of the cam member.
The reclining device according to claim 2.