JP2021172145A - Seat lifter device - Google Patents

Abstract

To provide a sheet lifter device that is able to appropriately absorb excessive load input from an output side.SOLUTION: A seat lifter device with an output shaft 22 for raising and lowering a seat has: a support portion rotatably supporting the output shaft 22; a lock portion that locks rotation of the output shaft 22 relative to the support portion; and an energy absorbing portion E1 provided in a power transmission path between the support portion and the output shaft 22 via the lock portion. The energy absorbing portion 1 is plastically deformed when a large load with a predetermined magnitude or more in a rotating direction is input to the output shaft 22 from the seat side.SELECTED DRAWING: Figure 37

Description

The present invention relates to a seat lifter device. More specifically, the present invention relates to a seat lifter device provided with an output shaft for raising and lowering the seat.

It is known that a vehicle seat is provided with a seat lifter device capable of adjusting the seat height of the seat cushion (Patent Document 1). Specifically, the seat lifter device transmits the operation movement amount as the feed rotation movement amount of the gear by raising or lowering the operation handle, and raises or lowers the seat surface height by a certain amount. It has become. Then, the seat lifter device is in an initial state in which the rotation of the gear is locked at that position when the operation of the operation handle is released, and the operation handle is returned to the neutral position before the operation by urging to be re-operated. It is supposed to be returned to.

The feed rotation of the gear accompanying the operation of the operation handle is performed by pushing and moving the feed claw meshed with the gear in the operation direction of the operation handle. Further, the rotation lock of the gear when the operation of the operation handle is released is performed as follows. That is, one of the lock poles having a pair of symmetrical structures meshed with the gears is removed by operating the operation handle, and the other is a ratchet type that allows rotation to escape in the feed direction but bites in the opposite direction. It has a meshing structure, and when the operation of the operation handle is released, the other party stops the rotation of the gear at that position.

Like the lock pole, the feed claw that rotates the feed of the gear has a pair of symmetrical claw structures so as to allow the movement of the operation handle to be returned to the neutral position when the operation is released. As the operation handle is operated, one is disengaged from the gear and the other meshes with the gear so that power can be transmitted in the feed direction, but the rotation is released in the opposite direction, which is a ratchet type meshing structure.

Japanese Unexamined Patent Publication No. 2016-78850

When an excessive load due to the occurrence of a vehicle collision or the like is input to the vehicle seat, the excessive load may be transmitted from the seat lifter device held in the locked state to the seat frame. Therefore, the present invention provides a seat lifter device capable of appropriately absorbing an excessive load input from the output side.

In order to solve the above problems, the seat lifter device of the present invention takes the following means.

That is, the seat lifter device of the present invention is a seat lifter device provided with an output shaft for raising and lowering the seat. This seat lifter device has a support portion that supports the output shaft so as to be rotatable, a lock portion that locks the rotation of the output shaft with respect to the support portion, and a power transmission path between the support portion and the output shaft via the lock portion. It has an energy absorbing unit provided in the. The energy absorbing unit is plastically deformed when a large load in the rotation direction of a predetermined size or more is input to the output shaft from the seat side.

According to the above configuration, the energy absorbing unit can appropriately absorb the excessive load input from the seat side to the output shaft.

Further, the seat lifter device of the present invention may be further configured as follows. The power transmission path revolves while rotating along the planetary carrier that is integrally connected to the output shaft and the internal gear that is rotatably connected to the planetary carrier and formed on the support portion as the output shaft rotates. It is composed of a planetary gear mechanism including a plurality of planetary gears, and a rotating member including a sun gear that meshes with the plurality of planetary gears and rotates in conjunction with the rotation, and whose rotation is locked by a lock portion. An energy absorbing portion is formed in a fitting portion that is axially fitted to the output shaft of the planetary carrier.

According to the above configuration, even if a planetary gear mechanism for accelerating the rotation of the output shaft is provided, the excess input from the seat side to the output shaft between the output shaft and the planetary carrier, which does not require accelerating. Can absorb various loads appropriately.

Further, the seat lifter device of the present invention may be further configured as follows. The energy absorbing part is a deformed part that plastically deforms in the rotational direction when a large load in the rotational direction of a predetermined size or more is input to the output shaft, and a deformed part that stops the deformation of the plastically deformed deformed part at a fixed position. It has a stop portion having a higher structural strength than that of the other.

According to the above configuration, it is possible to prevent the deformed portion from being excessively deformed by the stop portion while appropriately deforming the deformed portion with the rotation of the output shaft. As a result, it is possible to appropriately absorb the excessive load input from the seat side without significantly changing the posture of the seat.

Further, the seat lifter device of the present invention may be further configured as follows. The output shaft is provided in a state where the gap in the rotation direction is closed with respect to the deformed portion.

According to the above configuration, the deformed portion can be deformed from an early stage with the rotation of the output shaft, and an excessive load input from the seat side can be absorbed more appropriately.

Further, the seat lifter device of the present invention may be further configured as follows. The output shaft is connected to the power transmission section forming the power transmission path by spline fitting. The deformed portion has a predetermined size due to the formation of a lightening portion in the intermediate portion in the power transmission portion, which is separated from the contact surface between the teeth of the output shaft and the teeth of the output shaft in the rotational direction in the rotational direction. It has a fragile configuration that plastically deforms in the rotational direction when a large load in the rotational direction is input.

According to the above configuration, the energy absorbing portion can be rationally and appropriately formed by using the configuration of the spline fitting portion between the output shaft and the power transmission portion.

Further, the seat lifter device of the present invention may be further configured as follows. The energy absorbing unit is configured to be plastically deformed by inputting a large load in the rotation direction having a predetermined size or more with respect to the bidirectional rotation of the output shaft in the rotation direction.

According to the above configuration, it is possible to appropriately absorb an excessive load in both rotation directions input from the seat side to the output shaft.

It is an outside side view which showed the schematic structure of the seat lifter device which concerns on 1st Embodiment. It is a side view which looked at the structure on the outer side surface side from the inside in the sheet width direction. It is an exploded perspective view which shows the state which the operation handle and the rotation control device were removed from the side frame of a seat cushion. It is a perspective view which looked at the rotation control device from the outside in the seat width direction. It is a perspective view which looked at the rotation control device from the inside in the seat width direction. It is a front view which looked at the rotation control device from the outside in the seat width direction. FIG. 6 is a sectional view taken along line VII-VII of FIG. FIG. 6 is a sectional view taken along line VIII-VIII of FIG. It is an exploded perspective view which looked at the rotation control device from the outside in the seat width direction. 9 is an exploded perspective view of FIG. 9 as viewed from the inside in the seat width direction. It is an exploded perspective view which shows the state which partially assembled the component parts of a rotation control device. FIG. 11 is an exploded perspective view seen from the inside in the seat width direction. It is an exploded perspective view which shows the state in which the component parts of a rotation control device were further partially assembled. FIG. 13 is an exploded perspective view seen from the inside in the seat width direction. FIG. 5 is an exploded perspective view showing a state in which the components of the rotation control device are partially assembled to an assembly partner different from that in FIG. FIG. 15 is an exploded perspective view seen from the inside in the seat width direction. Further, it is an exploded perspective view showing a state in which the component parts of the rotation control device are partially assembled. FIG. 5 is an exploded perspective view showing a state in which the components of the rotation control device are partially assembled to an assembly partner different from that in FIG. It is a schematic diagram which showed the state of the feed part when the operation handle is in a neutral position. It is a schematic diagram which showed the state of the lock part when the operation handle is in a neutral position. It is a schematic diagram showing the state of the feed part when the operation handle is pushed down from a neutral position. It is a schematic diagram which showed the state of the lock part when the operation handle was pushed down from a neutral position. It is a schematic diagram showing the state of the lock part when the operation handle is further pushed down. It is a schematic diagram showing the state of the feed part when the operation handle is returned to the neutral position. It is a schematic diagram showing the state of the lock part when the operation handle is returned to the neutral position. It is a schematic diagram which showed the state of the feed part when the operation handle was pulled up from a neutral position. It is a schematic diagram which showed the state of the lock part when the operation handle was pulled up from a neutral position. It is a schematic diagram showing the state of the lock part when the operation handle is further pulled up. It is a schematic diagram showing the state of the feed part when the operation handle is returned to the neutral position. It is a schematic diagram showing the state of the lock part when the operation handle is returned to the neutral position. It is a front view which showed the state of the input part when the operation handle is in a neutral position. It is a front view which showed the state of the input part when the operation handle was pushed down to the maximum position. It is a front view which showed the state of the input part when the operation handle was pulled up to the maximum position. It is an enlarged view of the XXXIV part of FIG. 8 showing the friction suppression state of the friction generating part. It is an enlarged view corresponding to FIG. 34 which showed the state which the friction generating part was switched to the friction-on state. It is an enlarged view of the connection part of an output shaft and a planetary carrier. FIG. 6 is an enlarged view corresponding to FIG. 36 showing a state in which a large load in the clockwise direction is input to the output shaft and the planetary carrier is plastically deformed. FIG. 6 is an enlarged view corresponding to FIG. 36 showing a state in which a large load in the counterclockwise direction is input to the output shaft and the planetary carrier is plastically deformed. It is an exploded perspective view which showed the schematic structure of the seat lifter device which concerns on 2nd Embodiment. It is an enlarged view of the main part which showed the schematic structure of the seat lifter device which concerns on other embodiment. It is an enlarged view of the main part which showed the schematic structure of the seat lifter device which concerns on other embodiment. It is an enlarged view of the main part which showed the schematic structure of the seat lifter device which concerns on other embodiment. It is an enlarged view of the main part which showed the schematic structure of the seat lifter device which concerns on other embodiment. It is an enlarged view of the main part which showed the schematic structure of the seat lifter device which concerns on other embodiment.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.

<< First Embodiment >>
First, the configuration of the seat lifter device 10 according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 38. In the following description, when each direction such as front-back, up-down, left-right, etc. is shown, it means each direction shown in each figure. Further, when the term "seat width direction" is used, it refers to the left-right direction of the sheet 1 described later.

<About the schematic configuration of the seat lifter device 10>
The seat lifter device 10 according to the present embodiment is applied to the seat 1 of an automobile. As shown in FIGS. 1 and 2, the seat 1 includes a seat back 2 serving as a backrest portion of a seated occupant and a seat cushion 3 serving as a seating portion. The seat back 2 is connected to the rear end of the seat cushion 3 via a recliner (not shown) so that the backrest angle can be adjusted. The seat cushion 3 is connected to the floor F of the vehicle via an electric seat slide device 4 having a pair of left and right rail structures so that the position can be adjusted in the front-rear direction.

Further, the seat cushion 3 has a configuration in which an electric seat lifter device 10 having a pair of left and right link structures is connected to the seat slide device 4 having a pair of left and right rail structures. By connecting via the seat lifter device 10, the seat cushion 3 can also adjust the position in the height direction with respect to the floor F.

The seat slide device 4 is known and includes a pair of left and right lower rails 4a extending in the front-rear direction and a pair of left and right upper rails 4b assembled so as to be slidable in the front-rear direction with respect to each lower rail 4a. .. The pair of left and right lower rails 4a are fixed on the floor F via a pair of front and rear legs 4c, respectively.

The seat lifter device 10 includes a support bracket 14 fixed on each upper rail 4b, and a pair of front and rear link members 11 connected between each support bracket 14 and each side frame 3a of the seat cushion 3. With the above connection, the seat lifter device 10 includes a pair of left and right four-bar link mechanisms 12 in which a pair of front and rear link members 11 each perform a link motion between the side frame 3a on each side and the support bracket 14. Will be done.

As shown in FIG. 2, of the four front, rear, left, and right link members 11, the right rear link member 11 is a sector gear that meshes with the pinion gear 22a of the rotation control device 18 attached to the right side frame 3a. 11a is formed. With the above configuration, the link member 11 on the right rear side is configured to link by receiving the transmission of the rotational driving force from the pinion gear 22a. The upper right end of the link member 11 on the right rear side is connected to the right side frame 3a via a torque rod 17 so as to be rotatable.

The torque rod 17 is integrally bridged between the upper ends of the link member 11 on the right rear side and the link member 11 on the left rear side, and both link members 11 are driven and rotated synchronously. ing. When both rear link members 11 simultaneously link, the front link members 11 forming the four-section link mechanism 12 also link synchronously. As a result, the position of the seat cushion 3 in the height direction with respect to the floor F is adjusted.

The rotation control device 18 is assembled on the right side surface portion of the right side frame 3a. Specifically, the rotation control device 18 inserts the pinion gear 22a through the through hole 3a1 formed in the right side frame 3a and meshes it with the sector gear 11a located on the left side of the side frame 3a. It is assembled in. As shown in FIG. 3, the rotation control device 18 is assembled with an operation handle 5 extending forward.

The operation handle 5 is provided so as to extend forward from the rear right side of the seat cushion 3, and is configured so that the user can perform an operation of raising and lowering from the neutral position. By raising and lowering the operation handle 5 from the neutral position, the rotational force in each operation direction is input to the rotation control device 18. As a result, the rotational force in each operating direction is transmitted to the pinion gear 22a formed on the output shaft 22 of the rotation control device 18, and the link member 11 on the right rear side is moved in the rotational direction according to each operating direction.

Specifically, the rotation control device 18 is configured to hold the operation handle 5 in a neutral position and hold the output shaft 22 in a stopped state at all times before the operation handle 5 is operated. NS. The rotation control device 18 outputs a rotational force in the direction of raising the link member 11 on the right rear side to the front side to the pinion gear 22a by operating the operation handle 5 so as to be pulled up from the neutral position. As a result, the seat cushion 3 is pulled up from above the floor F.

Further, the rotation control device 18 outputs a rotational force in the direction of tilting the link member 11 on the right rear side to the rear side to the pinion gear 22a by operating the operation handle 5 so as to be pushed down from the neutral position. .. As a result, the seat cushion 3 is pushed down onto the floor F. Further, the rotation control device 18 returns the operation handle 5 to the neutral position while stopping the pinion gear 22a at the rotation position by releasing the operation state after the operation handle 5 is raised and lowered from the neutral position. It is designed to work.

<About the schematic configuration of the rotation control device 18>
Hereinafter, a specific configuration of the rotation control device 18 will be described with reference to FIGS. 4 to 38. In the following description, among the members constituting the rotation control device 18, any of FIGS. 4 to 38 shall be appropriately referred to for reference numerals not shown in the reference drawings. Each member constituting the rotation control device 18 is made of a pressed metal member.

As shown in FIGS. 4 to 8, the rotation control device 18 is composed of a substantially disk-shaped unit whose axial direction is directed in the seat width direction. The rotation control device 18 has an input portion N that is integrally assembled with the operation handle 5 shown in FIG. 3, and a support portion S that is integrally assembled with the right side frame 3a.

Further, the rotation control device 18 has an output shaft 22 that receives the rotational force from the input unit N, and a feed unit A that transmits the rotational force from the input unit N to the output shaft 22. Further, the rotation control device 18 is between the lock unit B that locks the rotation of the output shaft 22 when the rotational force is not transmitted from the input unit N and the lock unit B that accelerates the rotation of the output shaft 22. It has a speed-increasing portion U that transmits to the power transmission path of the above. Further, the rotation control device 18 has a friction generating portion G that exerts a frictional force on the rotation of the output shaft 22.

Specifically, as shown in FIGS. 9 to 18, the input unit N is composed of a substantially disk-shaped outer lever 41 and an inner lever 53. The outer lever 41 and the inner lever 53 are integrally assembled side by side on the central axis C extending in the seat width direction with the cover 24 described later sandwiched between them.

The support portion S is composed of a substantially disk-shaped main body base 23, a substantially ring plate-shaped intermediate base 25, and a substantially disk-shaped cover 24. The main body base 23, the intermediate base 25, and the cover 24 are configured to be integrally arranged side by side on the central axis C extending in the seat width direction.

The feed portion A is composed of four feed claws 52 and a substantially disk-shaped rotation transmission plate 36. Each of the four feed claws 52 is configured to be rotatably assembled to the inner lever 53 described above. The rotation transmission plate 36 has a configuration in which the output shaft 22 is inserted through the central portion (the portion through which the central axis C passes) and is integrally assembled. Further, the rotation transmission plate 36 is assembled so as to be able to rotate relative to the inner lever 53 along the central axis C extending in the seat width direction and around the central axis C.

As shown in FIG. 19, the rotation transmission plate 36 is configured to be integrally connected to the inner lever 53 in both the rotation direction by engaging the four feed claws 52 with the internal gear 36a. NS. As shown in FIGS. 21 and 26, the rotation transmission plate 36 has a pair of four feed claws 52 described later when the inner lever 53 is rotated in either direction from the neutral position. Is disengaged from the mesh with the internal gear 36a, and is fed in the rotational direction of the inner lever 53 by meshing with the remaining pair.

Due to the above rotation, the rotation transmission plate 36 feeds the output shaft 22 integrally assembled with the output shaft 22 in the corresponding rotation direction. Then, as shown in FIGS. 24 and 29, when the rotation of the operated inner lever 53 is returned, the rotation transmission plate 36 leaves itself at the position where the rotation operation is performed, and only the inner lever 53 is operated before the operation. It is possible to return to the initial position (neutral position) of. That is, as shown in FIGS. 21 and 26, the rotation transmission plate 36 is fed in the rotation direction by turning the inner lever 53 from the neutral position in either direction. Then, the rotation transmission plate 36 is temporarily locked by locking the output shaft 22 by the lock portion B described later at the position where the above operation is stopped.

However, as shown in FIGS. 24 and 29, when the inner lever 53 is returned from the locked position to the initial position (neutral position) before the operation, the rotation transmission plate 36 engages with the pair of feed claws 52. By sliding, only the inner lever 53 can be returned to the initial position before the operation together with each feed claw 52 while leaving itself in the locked position.

As shown in FIGS. 9 to 18, the lock portion B is composed of four poles 32 and a substantially ring plate-shaped rotating ring 37. Each of the four poles 32 is configured to be rotatably assembled to the intermediate base 25 described above. The rotating ring 37 is gear-connected to the output shaft 22 via a planetary gear mechanism 64 that constitutes the speed-increasing portion U so that power can be transmitted. As shown in FIG. 20, the four poles 32 are configured to lock the rotation of the rotating ring 37 with respect to the intermediate base 25 by meshing with the internal gear 37a of the rotating ring 37.

The lock locks the rotation of the output shaft 22 gear-connected to the rotating ring 37. As shown in FIGS. 22 and 27, the four poles 32 correspond to any pair via the control plate 56 described later by turning the outer lever 41 described above from the neutral position in either direction. Is disengaged from the meshing of the rotating ring 37 with the internal gear 37a. As a result, the remaining pairs of the four poles 32 are in a state of allowing the rotation ring 37 to rotate in the corresponding direction, and as shown in FIGS. 23 and 28, the rotation ring 37 and the output shaft 22 correspond to each other. It is in a state of allowing rotation in the direction in which it is used.

Then, when the rotation of the operated outer lever 41 is returned, the pair of poles 32 meshing with the internal gear 37a of the four poles 32 prevent the rotation ring 37 from rotating in the return direction. , The rotating ring 37 and the output shaft 22 are held in the locked state. Then, as shown in FIGS. 25 and 30, the four poles 32 are returned to a state in which the remaining pairs are also meshed with the internal gear 37a of the rotating ring 37 by returning the rotation of the outer lever 41, and the rotating ring 37 is returned. The bidirectional rotation of is locked.

As shown in FIGS. 9 to 18, the speed-increasing portion U includes a substantially disk-shaped planetary carrier 62, three planetary gears 63, an internal gear 23e formed on the main body base 23, and a sun gear in the center. It is composed of a rotating plate 38 having 38c and a rotating plate 38. The planet carrier 62 is configured such that the output shaft 22 is inserted through the central portion (the portion through which the central axis C passes) and is integrally assembled. Each of the three planetary gears 63 is configured to be rotatably assembled to the planetary carrier 62. Here, the rotating plate 38 corresponds to the "rotating member" of the present invention.

The rotary plate 38 is gear-connected so that the sun gear 38c at the center thereof can transmit power to the three planetary gears 63 by inserting the output shaft 22 through the central portion (the portion through which the central axis C passes). It is considered to be a configuration. Further, the rotating plate 38 has a configuration in which the outer peripheral portion thereof is fitted inside the rotating ring 37 described above and integrally assembled.

Each of the three connected planetary gears 63 is set in a gear-connected state so that power can be transmitted to the internal gear 23e formed on the main body base 23. As a result, the three planetary gears 63 revolve while rotating along the internal gear 23e of the main body base 23 via the planetary carrier 62 when the output shaft 22 is rotated from the neutral position in either direction. It has become. Then, as the three planetary gears 63 rotate, the rotary plate 38 having the sun gear 38c gear-connected to the center thereof is rotated in the same rotation direction as the output shaft 22.

At that time, the rotating plate 38 is accelerated and rotated so as to rotate at a speed faster than the output shaft 22 depending on the gear ratio of each gear. By the above rotation, the rotating plate 38 rotates the rotating ring 37 integrally assembled with the rotating plate 38 in the corresponding rotation direction. As described above, the rotation of the output shaft 22 is accelerated by the speed increasing portion U and transmitted to the rotating ring 37, so that the friction generating portion G, which will be described later, applies a frictional force to the rotating ring 37 to cause the rotating ring 37 to slide. The action of preventing the above can be effectively enhanced.

The friction generating portion G is composed of three friction clutches 58, a substantially wave washer-shaped leaf spring 59, and a substantially ring plate-shaped pressure receiving plate 61. Each of the three friction clutches 58 is assembled so as to be rotatable and axially movable with respect to the intermediate base 25.

As shown in FIGS. 7 to 8 and 34, the leaf spring 59 and the pressure receiving plate 61 are set so as to be stacked on the inner side surface (left side surface) of the cover 24 in order. Specifically, the leaf spring 59 is set so as to be sandwiched in the axial direction between the pressure receiving plate 61 and the cover 24. Further, the pressure receiving plate 61 is set so that the above-mentioned rotating ring 37 and the ring plate shapes of each other are overlapped with each other in the axial direction. Further, the leaf spring 59 and the pressure receiving plate 61 are set in a state in which their outer peripheral portions are engaged with the main body base 23 to prevent rotation.

The pressure receiving plate 61 is configured to be constantly subjected to the action of an axial pressing force (elastic force) with the cover 24 as a fulcrum from a leaf spring 59 that is pressed and sandwiched between the cover 24 and the cover 24. As a result, the pressure receiving plate 61 is always held in a state of being pressed against the rotating ring 37 in the axial direction (leftward direction). Due to the pressing force, a frictional force is applied to the rotating ring 37 with respect to the rotation.

As shown in FIG. 21, the three friction clutches 58 are radial in the radial direction by the control plate 56 when the control plate 56 described above is turned in the direction of pushing down the output shaft 22 (clockwise in the figure) by the operation of the outer lever 41. It is configured to be pushed out of the. By the above extrusion, as shown in FIG. 35, each of the three friction clutches 58 rides on the inclined surface 24j formed on the cover 24, presses the leaf spring 59 in the axial direction (left direction), and rotates. The frictional force applied to the ring 37 is increased.

As shown in FIGS. 9 to 18, the rotation control device 18 further includes a control plate 56 integrally having an inner and outer double ring plate shape. The control plate 56 is configured to be rotatably supported by the output shaft 22 by inserting the output shaft 22 into the central portion (the portion through which the central axis C passes). Further, the control plate 56 is configured such that an arm 41c extending from the outer lever 41 is fitted into the outer peripheral portion thereof and is integrally assembled with the outer lever 41.

As shown in FIGS. 21 and 26, the control plate 56 rotates integrally with the outer lever 41 by turning the outer lever 41 in either direction from the neutral position, and the above-mentioned four poles 32 One of the corresponding pairs is operated so as to be disengaged from the internal gear 37a of the rotating ring 37. Further, the control plate 56 does not move the three friction clutches 58 when the outer lever 41 is turned in the direction of pulling up the output shaft 22 as shown in FIG. 26, but the direction of pushing down the output shaft 22 as shown in FIG. When it is turned to, the three friction clutches 58 are operated so as to be pushed outward in the radial direction.

As a result, as shown in FIG. 35, the three friction clutches 58 press the leaf spring 59 in the axial direction (leftward direction) with the cover 24 as a fulcrum to increase the frictional force applied to the rotating ring 37. As described above, since a large frictional force is applied to the rotation of the output shaft 22 in the pushing direction, it is effective that the output shaft 22 slides in the pushing direction due to the action of its own weight applied to the seat 1. It is possible to suppress it.

As shown in FIGS. 9 to 18, the rotation control device 18 has torsion springs 35, 43, 55 in addition to the above. The torsion spring 35 is hooked between the outer lever 41 and the cover 24 described above, and the outer lever 41 is urged to a neutral position with respect to the cover 24.

The torsion spring 43 is hooked between the front and rear pairs of the four feed claws 52 described above, and urges each feed claw 52 in the rotational direction to mesh with the internal gear 36a of the rotation transmission plate 36. It is said that. The torsion spring 55 is hooked between the front and rear pairs of the four poles 32 described above, and is configured to urge each pole 32 in the rotational direction to mesh with the internal gear 37a of the rotary ring 37. ..

<Specific configuration of each part of the rotation control device 18>
Subsequently, the details of each member constituting the rotation control device 18 will be described. First, the configurations of the outer lever 41 and the inner lever 53 constituting the input unit N will be described with reference to FIG. 9 and the like. The outer lever 41 is composed of a substantially disk-shaped member whose surface is directed in the seat width direction. The above-mentioned operation handle 5 is integrally assembled with the outer lever 41.

A central hole 41a is formed in the central portion of the outer lever 41 (a portion through which the central axis C passes) so as to penetrate in a round hole shape in the axial direction. A cylindrical fourth shaft portion 22g forming an end on the right side (outside in the seat width direction) of the output shaft 22 is passed through the center hole 41a from the left side and fitted so as to be rotatable (FIG. 7). -See FIG. 8). Further, in the middle portion of the disk portion of the outer lever 41, a through hole 41b that penetrates in a round hole shape in the axial direction is formed at a symmetrical position in the circumferential direction.

A pair of stopper pins 53b, which are passed through the inner lever 53 from the left side, are passed through the through holes 41b from the left side and are integrally connected to the inner lever 53. As a result, the outer lever 41 is integrally coupled with the inner lever 53.

Further, on the peripheral edge of the outer lever 41, an arm 41c that is bent at a right angle in the axial direction (left direction) and projects at two positions above and below the outer lever 41 is formed. These arms 41c are integrally inserted into the corresponding insertion grooves formed on the outer peripheral portion of the control plate 56 from the right side through the corresponding through holes 24g formed in the cover 24 described later. It is matched. As a result, the outer lever 41 rotates integrally with the control plate 56.

As shown in FIG. 9 and the like, the inner lever 53 is composed of a substantially disk-shaped member whose surface is directed in the seat width direction. A central hole 53a is formed in the central portion of the inner lever 53 (a portion through which the central axis C passes) so as to penetrate in a round hole shape in the axial direction. A cylindrical third shaft portion 22f forming an axially intermediate portion of the output shaft 22 described above is passed through the central hole 53a from the left side and fitted so as to be rotatable (see FIGS. 7 to 8). ).

Further, in the middle portion of the disk portion of the inner lever 53, a through hole 53c that penetrates in a round hole shape in the axial direction is formed at a symmetrical position in the circumferential direction. A pair of stopper pins 53b are passed through these through holes 53c from the left side thereof and are integrally connected to each other. As a result, the inner lever 53 is integrally coupled with the outer lever 41.

In the middle portion of the disk portion of the inner lever 53, shaft pins 53d protruding in the axial direction (right direction) in a round pin shape are formed at four positions in the circumferential direction. The four feed claws 52 described above are fitted into these shaft pins 53d from the right side and connected so as to be rotatable.

Next, the configurations of the main body base 23, the intermediate base 25, and the cover 24 constituting the support portion S will be described with reference to FIG. 9 and the like. The main body base 23 is composed of a substantially disk-shaped member whose surface is directed in the seat width direction. At the center of the main body base 23, an internal gear 23e that has been half-punched into a shape that is extruded into a substantially cylindrical shape in the axial direction (right direction) is formed.

On the inner peripheral surface of the internal gear 23e, internal teeth capable of engaging the three planetary gears 63 described above so as to be able to transmit power are formed endlessly over the entire circumference. A central hole 23c is formed in the central portion (a portion through which the central axis C passes) of the internal gear 23e of the main body base 23 so as to penetrate in a round hole shape in the axial direction. A pinion gear 22a formed at the left end (inside in the seat width direction) of the output shaft 22 is passed through the center hole 23c from the right side (outside in the seat width direction), and is intermediate in the axial direction of the output shaft 22. The columnar first shaft portion 22b forming the portion is fitted so as to be rotatable (see FIGS. 7 to 8).

By the above assembly, the output shaft 22, the above-mentioned planetary carrier 62 and the three planetary gears 63 to be assembled to the output shaft 22 are set in the accommodating recess 23b forming the region in the internal gear 23e of the main body base 23, respectively. NS. Specifically, the three planetary gears 63 are set in a state of being meshed with the internal gear 23e of the main body base 23 so as to be able to transmit power.

As shown in FIG. 9 and the like, a seat portion 23a in which the above-mentioned rotating ring 37 is set in the axial direction is formed in a portion of the main body base 23 that projects from the periphery of the internal gear 23e. .. Locking claws 59a and 61a projecting from the corresponding three peripheral positions of the leaf spring 59 and the pressure receiving plate 61 are fitted in the axial direction at the three peripheral positions of the seat portion 23a and integrated in the rotational direction. A locking portion 23d that can be locked in such a state is formed.

The main body base 23 is set so that the intermediate base 25 and the cover 24 described above are stacked in order from the right side (outside in the seat width direction) in the axial direction on the portion protruding from the periphery of the internal gear 23e. And bolted (not shown) and integrally connected. The main body base 23 is also bolted (not shown) to the right side frame 3a described above to be integrally connected.

The intermediate base 25 is composed of a substantially ring plate-shaped member whose surface is directed in the seat width direction. The intermediate base 25 is formed with shaft pins 25b protruding in the axial direction (leftward direction) in a round pin shape at four positions in the circumferential direction of the seat portion 25a forming the ring plate shape. The four poles 32 described above are fitted into the shaft pins 25b from the left side and connected so as to be rotatable.

Further, the intermediate base 25 is formed with through holes 25c penetrating in a round hole shape in the axial direction at three positions in the circumferential direction of the seat portion 25a. Shaft pins 58a projecting in the axial direction (right direction) of the three friction clutches 58 described above are fitted into the through holes 25c from the left side and connected so as to be rotatable.

The cover 24 is composed of a substantially disk-shaped member whose surface faces in the seat width direction. The cover 24 is formed with a flange 24h that projects substantially in a cylindrical shape in the axial direction (leftward direction) from the outer peripheral edge thereof. The cover 24 has seats 24d in which two overhanging ends of the flange 24h are bent at right angles to the outer peripheral side, and these seats 24d are applied to the periphery of the main body base 23 described above and fastened with bolts ( By being shown (not shown), it is integrally connected to the cover 24. By the above coupling, the cover 24 is set in a state of wrapping each component such as the feed portion A and the lock portion B between the cover 24 and the main body base 23 (see FIGS. 4 to 5).

Further, as shown in FIG. 9 and the like, a central hole 24a penetrating in the axial direction in a round hole shape is formed in the central portion (the portion through which the central axis C passes) of the disk of the cover 24. A cylindrical fourth shaft portion 22g forming an end on the right side (outside in the seat width direction) of the output shaft 22 is passed through the center hole 24a from the left side and fitted so as to be rotatable (FIG. 7). -See FIG. 8).

Further, as shown in FIG. 9 and the like, an engaging piece 24b cut up at a right angle so as to project in the axial direction (right direction) is formed on the peripheral edge of the disk portion of the cover 24. One of the pair of arms 41c projecting from the peripheral edge of the outer lever 41 is set on the engaging piece 24b so as to be overlapped inward in the radial direction.

Then, each end of the torsion spring 35 is hooked between the arm 41c and the engaging piece 24b. By engaging the torsion spring 35, the outer lever 41 is constantly urged so that the arrangement of the arm 41c in the circumferential direction with respect to the engaging piece 24b is the same, and is held in a neutral position with respect to the cover 24.

As shown in FIG. 10 and the like, a riding portion 24c is formed on the peripheral edge of the disk portion of the cover 24 so as to project at an axial direction (leftward) from a symmetrical position in the circumferential direction. There is. As shown in FIG. 19, these riding portions 24c are set so as to be inserted between the upper and lower pairs of the four feed claws 52 described above.

As shown in FIG. 21, each riding portion 24c is located on the upper left side and the lower right side of the four feed claws 52 when the inner lever 53 is turned in the direction of pushing down the output shaft 22 (clockwise in the figure). The two feed claws 52 are placed on their edges to disengage the two feed claws 52 from meshing with the internal gear 36a of the rotation transmission plate 36. Further, as shown in FIG. 24, each riding portion 24c engages the two feed claws 52 disengaged from the above meshing with the internal gear 36a of the rotation transmission plate 36 by returning the rotated operation of the inner lever 53. Return to the original state.

Similarly, as shown in FIG. 26, each riding portion 24c is located on the upper right side of the four feed claws 52 when the inner lever 53 is turned in the direction in which the output shaft 22 is pulled up (counterclockwise in the figure). The two feed claws 52 on the lower left side are put against their edges, and these two feed claws 52 are disengaged from the meshing with the internal gear 36a of the rotation transmission plate 36. Further, as shown in FIG. 29, each riding portion 24c engages the two feed claws 52 disengaged from the above meshing with the internal gear 36a of the rotation transmission plate 36 by returning the rotated operation of the inner lever 53. Return to the original state.

As shown in FIG. 10 and the like, in the middle portion of the disk portion of the cover 24, a guide hole 24e penetrating in the axial direction in an arcuate shape drawn around the central axis C is provided at a symmetrical position in the circumferential direction. It is formed. Each stopper pin 53b, which is passed in the axial direction across the outer lever 41 and the inner lever 53 described above, is passed through the guide holes 24e from the left side.

The outer lever 41 and the inner lever 53 are integrally pushed down from the neutral position (see FIG. 31) or pulled up (see FIG. 32) in each of the guide holes 24e due to the shape of the holes extending in an arc shape (see FIG. 33). (See) It is designed to let the movement escape. Each guide hole 24e is adapted to lock the raising / lowering operation of the outer lever 41 and the inner lever 53 at the respective positions where the stopper pins 53b hit the ends of the holes extending in an arc shape (FIGS. 32 to 32). 33).

As shown in FIG. 9 and the like, through holes 24f are formed on the peripheral edge of the disk portion of the cover 24 at three positions in the circumferential direction so as to penetrate in a round hole shape in the axial direction. Each of the shaft pins 58a protruding in the axial direction (right direction) from the three friction clutches 58 described above in a round pin shape can be passed through the through holes 24f from the left side.

As shown in FIG. 10 and the like, at the peripheral edge of the disk portion of the cover 24, through holes 24g penetrating in the axial direction in an arc shape drawn around the central axis C are provided at two positions above and below the disk portion. It is formed. The upper one of the through holes 24g is formed at an overlapping position communicating with the cut-up hole of the engaging piece 24b described above.

The corresponding arms 41c projecting axially (leftward) from the peripheral edge of the outer lever 41 described above are passed through the through holes 24g from the right side. As a result, each through hole 24g allows the movement of each arm 41c to escape when the outer lever 41 is turned from the neutral position.

Next, the configurations of the four feed claws 52 constituting the feed portion A and the rotation transmission plate 36 will be described with reference to FIG. 9 and the like. Each of the four feed claws 52 is composed of an arm-shaped member whose surface faces in the seat width direction. In each feed claw 52, a central hole 52b formed at the base end portion thereof and penetrating in a round hole shape in the axial direction is fitted into each corresponding shaft pin 53d formed on the inner lever 53 described above from the right side. Are connected so that they can rotate.

As shown in FIG. 19, the four feed claws 52 are provided side by side with respect to the inner lever 53 so as to form a pair in the front-rear and up-down directions. Of the above four feed claws 52, the two feed claws 52 on the front upper side and the rear lower side each have a shape in which the arm extends in the counterclockwise direction shown in the drawing from the respective rotation center (axis pin 53d). Further, the remaining two feed claws 52 on the front lower side and the rear upper side each have a shape in which an arm extends in the clockwise direction shown in the drawing from each rotation center (axis pin 53d).

The four feed claws 52 are formed with external teeth 52a that can mesh with the internal gear 36a of the rotation transmission plate 36 at the tip ends of their arms. A torsion spring 43 is hooked between each pair of the front and rear of the four feed claws 52. Each torsion spring 43 is set so that a coiled portion at the center thereof is passed through each stopper pin 53b passed through the inner lever 53.

Then, the upper torsion spring 43 is set in a state in which one end and the other end thereof are pressed against the front upper feed claw 52 and the rear upper feed claw 52 in the urging direction for exerting elastic force, respectively. ing. The lower torsion spring 43 is in a state in which one end and the other end thereof are pressed against the front lower side feed claw 52 and the rear lower side feed claw 52 in the urging direction to exert elastic force, respectively. It is set to.

Due to the urging force of each torsion spring 43, each feed claw 52 is constantly pushed outward in the radial direction around each rotation center (axis pin 53d) as shown in FIG. The outer teeth 52a are held in a state of being meshed with the internal gear 36a of the rotation transmission plate 36. In the above four feed claws 52, the meshing force exerted by the external teeth 52a on the internal gear 36a of the rotation transmission plate 36 is the two feed claws 52 on the front upper side and the rear lower side, and the front lower side and the rear upper side 2. The two feed claws 52 have different configurations from each other.

Specifically, the two feed claws 52 on the front upper side and the rear lower side have the inner lever 53 in the clockwise direction shown from the neutral position as shown in FIG. 21 when their outer teeth 52a mesh with the internal gear 36a. By being turned in the (push-down direction), the internal gear 36a is configured to mesh in a state of being integrated in the rotation direction so that it can be pushed and turned in that direction. However, the two feed claws 52 on the front upper side and the rear lower side are for rotation in which the inner lever 53 is turned in the clockwise direction shown in the drawing and then returned to the initial position before the operation as shown in FIG. 24. The internal gear 36a is not integrated with the internal gear 36a, and is returned to the initial position before the operation while sliding on the internal gear 36a in the rotational direction.

On the other hand, returning to FIG. 19, the two feed claws 52 on the rear upper side and the front lower side show the inner lever 53 from the neutral position as shown in FIG. 26 when their outer teeth 52a mesh with the internal gear 36a. By being turned in the counterclockwise direction (pulling direction), the internal gear 36a is configured to mesh in a state of being integrated in the rotation direction so that it can be pushed and turned in that direction. However, the two feed claws 52 on the rear upper side and the front lower side are rotated with respect to the rotation in which the inner lever 53 is turned in the counterclockwise direction shown in the drawing and then returned to the initial position before the operation as shown in FIG. Is not integrated with the internal gear 36a, but is returned to the initial position before the operation while sliding on the internal gear 36a in the rotational direction.

With the above configuration, the four feed claws 52 can feed the rotation transmission plate 36 in the form of pushing the rotation transmission plate 36 in either direction regardless of the direction in which the inner lever 53 is turned from the neutral position. Then, when the inner lever 53 is returned to the neutral position from the position where the inner lever 53 is turned in each direction, the four feed claws 52 leave the rotation transmission plate 36 at the position where the rotation transmission plate 36 is turned and move the inner lever 53 to the initial position before the operation. Can be returned.

As shown in FIG. 21, the four feed claws 52 have two feed claws 52 on the rear upper side and the front lower side when the inner lever 53 is turned from the neutral position in the clockwise direction (pushing down direction) shown in the drawing. It is disengaged from the mesh with the internal gear 36a and is maintained in that state. Further, as shown in FIG. 26, when the inner lever 53 is turned from the neutral position in the counterclockwise direction (pulling direction) shown, the two feed claws 52 on the front upper side and the rear lower side are brought into contact with the internal gear 36a. It is designed to be disengaged and held in that state.

With such a configuration, when the inner lever 53 is returned from the position where it is turned in each direction to the neutral position, the two feed claws 52 that act to regulate the movement of the inner lever 53 are the inner lever 53. It is designed not to interfere with the returned movement. Specifically, as shown in FIG. 21, by turning the inner lever 53 from the neutral position in the clockwise direction (pushing down direction) shown, the two feed claws 52 on the rear upper side and the front lower side cover the above-mentioned cover. It is pressed against the edge of each of the riding portions 24c of 24 and turned so as to be disengaged from the mesh with the internal gear 36a. Then, the two feed claws 52 on the rear upper side and the front lower side are in a state of riding on each riding portion 24c while the inner lever 53 is being operated in the above direction, and from meshing with the internal gear 36a. It is held in the removed state.

Further, as shown in FIG. 26, when the inner lever 53 is turned from the neutral position in the counterclockwise direction (pulling direction) shown, the two feed claws 52 on the front upper side and the rear lower side are formed on the cover 24 described above. It is pressed against the edge of each riding portion 24c and turned so as to be disengaged from the mesh with the internal gear 36a. Then, the two feed claws 52 on the front upper side and the rear lower side are in a state of riding on each of the riding portions 24c while the inner lever 53 is being operated in the above direction, and from the engagement with the internal gear 36a. It is held in the removed state.

Returning to FIG. 19, the two feed claws 52 on the rear upper side and the front lower side are arranged so that their outer teeth 52a mesh with each other at a position offset by half a pitch from the teeth of the internal gear 36a. There is. Similarly, the two feed claws 52 on the front upper side and the rear lower side are also arranged so that their outer teeth 52a mesh with the teeth of the internal gear 36a at positions shifted by half a pitch from each other. With such a configuration, the backlash in the rotation direction that may occur between the outer teeth 52a of each feed claw 52 and the internal gear 36a when they are meshed with each other is suppressed to be small.

The rotation transmission plate 36 is composed of a substantially disk-shaped member whose surface faces in the seat width direction. At the center of the rotation transmission plate 36, an internal gear 36a that has been half-punched into a shape that is extruded into a substantially cylindrical shape in the axial direction (right direction) is formed. An internal gear-shaped spline hole 36b penetrating in the axial direction is formed in the central portion of the disk of the rotation transmission plate 36 (the portion through which the central axis C passes).

An external gear-shaped second spline 22e forming an intermediate portion in the axial direction of the output shaft 22 is passed through the spline hole 36b from the left side and fitted in a state of being integrated in the rotational direction. By the above fitting, the rotation transmission plate 36 is connected to the output shaft 22 in a state of being integrated in the rotation direction.

Next, the configurations of the four poles 32 and the rotating ring 37 constituting the lock portion B will be described with reference to FIG. 9 and the like. Each of the four poles 32 is composed of an arm-shaped member whose surface faces in the seat width direction. In each pole 32, a central hole 32b formed at the base end portion thereof and penetrating in a round hole shape in the axial direction is fitted into each corresponding shaft pin 25b formed in the intermediate base 25 described above from the left side. Are connected so that they can rotate.

As shown in FIG. 20, the four poles 32 are provided side by side with respect to the intermediate base 25 so as to form a pair in the front, rear, top and bottom, respectively. Of the above four poles 32, the two poles 32 on the front upper side and the rear lower side each have a shape in which the arm extends in the counterclockwise direction shown from the respective rotation center (axis pin 25b). Further, the remaining two poles 32 on the front lower side and the rear upper side each have a shape in which an arm extends in the clockwise direction shown in the drawing from each rotation center (axis pin 25b).

The four poles 32 are formed with external teeth 32a that can mesh with the internal gear 37a of the rotating ring 37 at the tip ends of their arms. A torsion spring 55 is hooked between the upper and lower pairs of the four poles 32, respectively.

Specifically, the front torsion spring 55 is set in a state in which one end and the other end are applied to the front upper pole 32 and the front lower pole 32 in the urging direction to exert elastic force, respectively. Has been done. Further, the torsion spring 55 on the rear side is set in a state in which one end and the other end thereof are applied to the upper rear pole 32 and the lower rear pole 32 in the urging direction to exert elastic force, respectively. There is.

Due to the urging force of each torsion spring 55, each pole 32 is constantly pushed outward in the radial direction around each center of rotation (axis pin 25b) as shown in FIG. 20, and outside of them. The teeth 32a are held in a state of being meshed with the internal gear 37a of the rotating ring 37. In the above four poles 32, the meshing force exerted by the external teeth 32a on the internal gear 37a of the rotating ring 37 is the two poles 32 on the front upper side and the rear lower side and the two poles 32 on the front lower side and the rear upper side. And, the configurations are different from each other.

Specifically, the two poles 32 on the front upper side and the rear lower side prevent the rotation of the rotating ring 37 in the clockwise direction (pushing down direction) by engaging the outer teeth 32a with the internal gear 37a. It is configured. However, in the two poles 32 on the front upper side and the rear lower side, even if their outer teeth 32a are meshed with the internal gear 37a, as shown in FIG. 28, the rotating ring 37 is in the counterclockwise direction (pulling direction) shown. ), The rotation ring 37 is configured to escape the rotation by sliding on the internal gear 37a.

On the other hand, returning to FIG. 20, the two poles 32 on the rear upper side and the front lower side are in the counterclockwise direction (pulling direction) of the rotating ring 37 by engaging the outer teeth 32a with the internal gear 37a. It is configured to prevent rotation. However, in the two poles 32 on the rear upper side and the front lower side, even if their outer teeth 32a mesh with the internal gear 37a, as shown in FIG. 23, the rotating ring 37 is shown in the clockwise direction (pushing down direction). When it is turned to, it slides on the internal gear 37a to allow the rotation of the rotating ring 37 to escape.

The four poles 32 are brought into the following states when the inner lever 53 is turned from the neutral position in the clockwise direction (pushing down direction) as shown in FIG. 21. That is, as shown in FIG. 22, by the above rotation, the two poles 32 on the front upper side and the rear lower side are disengaged from the mesh with the internal gear 37a by the control plate 56 and are held in that state. On the other hand, the two poles 32 on the rear upper side and the front lower side are left in a state of being meshed with the internal gear 37a. As a result, the four poles 32 are in a state where the rotation of the rotating ring 37 in the clockwise direction (pushing down direction) can be released (see FIG. 23).

The four poles 32 are engaged with the internal gear 37a when the operation of the inner lever 53 is returned to the neutral position as shown in FIG. 24 after the rotating ring 37 is rotated in the clockwise direction shown in the drawing. And two poles 32 on the lower front side prevent the rotation ring 37 from rotating in the counterclockwise direction shown in the drawing, and hold the rotation ring 37 in a fixed position (see FIG. 25). Then, when the operation of the inner lever 53 (see FIG. 24) is returned, the rotation of the control plate 56 is returned to the initial position, so that the two poles 32 on the front upper side and the rear lower side are moved as shown in FIG. It is returned to the initial state in which it meshes with the internal gear 37a.

On the other hand, the four poles 32 are brought into the following states when the inner lever 53 is turned from the neutral position in the counterclockwise direction (pulling direction) as shown in FIG. 26. That is, as shown in FIG. 27, due to the rotation, the two poles 32 on the rear upper side and the front lower side are disengaged from the mesh with the internal gear 37a by the control plate 56 and are held in that state. On the other hand, the two poles 32 on the front upper side and the rear lower side are left in a state of being meshed with the internal gear 37a. As a result, the four poles 32 are in a state where the rotation of the rotating ring 37 in the counterclockwise direction (pulling direction) can be released (see FIG. 28).

The four poles 32 are before meshing with the internal gear 37a when the operation of the inner lever 53 is returned to the neutral position as shown in FIG. 29 after the rotating ring 37 is turned in the counterclockwise direction shown in the drawing. Two poles 32 on the upper side and the lower rear side prevent the rotating ring 37 from rotating in the clockwise direction shown in the drawing, and hold the rotating ring 37 in place (see FIG. 30). Then, when the operation of the inner lever 53 (see FIG. 29) is returned, the rotation of the control plate 56 is returned to the initial position, so that the two poles 32 on the rear upper side and the front lower side are moved as shown in FIG. It is returned to the initial state in which it meshes with the internal gear 37a.

As shown in FIG. 9 and the like, the rotating ring 37 is composed of a substantially ring plate-shaped member whose surface is directed in the seat width direction. The rotating ring 37 is formed with an internal gear 37a that projects in a substantially cylindrical shape in the axial direction (rightward direction) at the inner peripheral portion of the ring plate. On the inner peripheral surface of the internal gear 37a, internal teeth capable of engaging the external teeth 32a of the four poles 32 described above are formed endlessly over the entire circumference. The rotating ring 37 is set so that the right side surface of the ring plate is in surface contact with the left side surface of the pressure receiving plate 61.

Next, the configurations of the planetary carriers 62, the three planetary gears 63, and the rotating plate 38 constituting the speed-increasing portion U will be described with reference to FIG. 9 and the like. The planetary carrier 62 is composed of a substantially disk-shaped member whose surface is directed in the seat width direction. An internal gear-shaped spline hole 62a penetrating in the axial direction is formed in the central portion (the portion through which the central axis C passes) of the planetary carrier 62.

An external gear-shaped first spline 22c forming an intermediate portion in the axial direction of the output shaft 22 is passed through the spline hole 62a from the left side and fitted in a state of being integrated in the rotational direction. By the above fitting, the planet carrier 62 is connected to the output shaft 22 in a state of being integrated in the rotational direction.

The planet carrier 62 is formed with shaft pins 62b protruding in the axial direction (right direction) in a round pin shape at three positions on the ring plate in the circumferential direction. Three planetary gears 63, which will be described later, are fitted into these shaft pins 62b from the right side and connected so as to be rotatable.

Each of the three planetary gears 63 is configured as a disk-shaped external gear whose surface faces in the seat width direction. In the three planetary gears 63, the central hole 63a formed in the central portion thereof and penetrating in a round hole shape in the axial direction is fitted into the corresponding shaft pin 62b of the planetary carrier 62 described above from the right side and can rotate. Are connected as follows.

The three planetary gears 63 are set in a state of being meshed with the internal gear 23e of the main body base 23 by assembling to the main body base 23 via the planet carrier 62 and the output shaft 22 (see FIG. 13 and the like). By the above assembly, the three planetary gears 63 revolve while rotating along the internal gear 23e of the main body base 23 by turning the output shaft 22 in either direction.

As shown in FIG. 9 and the like, the rotating plate 38 is composed of a substantially disk-shaped member whose surface is directed in the seat width direction. A central hole 38a that penetrates in the axial direction in a round hole shape is formed in the central portion (the portion through which the central axis C passes) of the rotating plate 38. A cylindrical second shaft portion 22d forming an axially intermediate portion of the output shaft 22 is fitted into the center hole 38a so as to be rotatable (see FIGS. 7 to 8).

Further, as shown in FIG. 10 and the like, a sun gear 38c protruding in the axial direction from the periphery of the central hole 38a is formed in the central portion of the rotating plate 38. The sun gear 38c is set between the three planetary gears 63 described above by setting the output shaft 22 in the center hole 38a, and is gear-connected to each planetary gear 63 so as to be able to transmit power. ..

As a result, the sun gear 38c rotates by receiving the transmission of the rotational driving force by rotating the three planetary gears 63 with the rotation of the output shaft 22. Specifically, the sun gear 38c is adapted to rotate by increasing the speed at which the three planetary gears 63 rotate in the internal gear 23e of the main body base 23 according to the meshing gear ratio.

On the outer peripheral portion of the rotating plate 38, meshing claws 38b that can mesh with the internal gear 37a of the rotating ring 37 are formed at a plurality of locations in the circumferential direction. The rotary plate 38 is set in the internal gear 37a so that the meshing claw 38b meshes with the internal gear 37a of the rotary ring 37. As a result, the rotating plate 38 is connected to the rotating ring 37 in a state of being integrated in the rotating direction. According to the above configuration, the rotating plate 38 is configured to rotate the rotating ring 37 at an increased rotational speed by rotating the sun gear 38c at the center of the rotating plate 38 as the output shaft 22 rotates.

Next, the configurations of the three friction clutches 58, the leaf springs 59, and the pressure receiving plate 61 constituting the friction generating portion G will be described with reference to FIG. 9 and the like. Each of the three friction clutches 58 is composed of an arm-shaped member whose surface faces in the seat width direction. At the base end of each friction clutch 58, a shaft pin 58a projecting in an axial direction (rightward direction) in a round pin shape is formed. Each of the shaft pins 58a is passed through each of the corresponding through holes 25c formed in the intermediate base 25 described above from the left side and is engaged with the shaft pins 58a so as to be rotatable and axially movable.

The three friction clutches 58 are formed with sliding portions 58b at the tip ends of their arms, which bulge in the axial direction (rightward direction) and come into surface contact with the inner side surface (left side surface) of the cover 24. As shown in FIG. 34, each sliding portion 58b is always in contact with the general surface inside (left side) of the cover 24. However, as described above in FIG. 21, each sliding portion 58b is moved from the inside to the outside in the radial direction by the control plate 56 when the inner lever 53 is turned from the neutral position in the clockwise direction (pushing down direction) shown in the drawing. Be pressed.

As a result, each friction clutch 58 is pushed outward in the radial direction around their center of rotation (shaft pin 58a) to cover their sliding portions 58b on the inner surface of the cover 24, as shown in FIG. (Left side surface) Ride on each corresponding inclined surface 24j formed at three positions in the circumferential direction. Specifically, each friction clutch 58 faces each inclined surface 58c formed in the outer peripheral region on the right side surface of each sliding portion 58b so as to be chamfered along the corresponding inclined surface 24j of the cover 24. Let them ride in contact with each other.

As a result, each sliding portion 58b is moved to the left side while being pushed outward in the radial direction along each inclined surface 24j of the cover 24. Due to the oblique movement, each sliding portion 58b pushes each portion that undulates to the right side of the leaf spring 59 that abuts on them from the left side to the left side.

By the above pushing, each sliding portion 58b exerts a force for pressing the pressure receiving plate 61 to the left side through the elastic force of the leaf spring 59, and slides on the rotation of the rotating ring 37 which comes into surface contact with the pressure receiving plate 61 from the left side. A dynamic friction resistance force is applied. On the other hand, the sliding portion 58b of each friction clutch 58 is not operated by the control plate 56 when the inner lever 53 is turned from the neutral position in the counterclockwise direction (pulling direction) shown in FIG. 26 as described above. As shown in 34, the cover 24 is kept in contact with the general surface inside (left side).

As shown in FIG. 9 and the like, the leaf spring 59 is composed of a substantially wave washer-shaped member whose surface is directed in the seat width direction. On the outer peripheral portion of the leaf spring 59, locking claws 59a are formed at three positions in the circumferential direction so as to project outward in the radial direction in a claw shape. The leaf spring 59 is mounted on the main body base 23 by fitting the locking claws 59a to the corresponding locking portions 23d formed on the seat portion 23a of the main body base 23 from the right side. They are connected in a state of being integrated in the direction of rotation.

The leaf spring 59 is configured to always exert a constant elastic force in the axial direction between the pressure receiving plate 61 and each friction clutch 58 due to its wavy shape. Then, as described above in FIG. 35, the leaf spring 59 is switched so that each friction clutch 58 is pushed outward in the radial direction and pressed from the right side to strengthen the elastic force acting on the pressure receiving plate 61. It is said that it is configured to be.

As shown in FIG. 9 and the like, the pressure receiving plate 61 is composed of a substantially ring plate-shaped member whose surface is directed in the seat width direction. Similar to the leaf spring 59, locking claws 61a are formed on the outer peripheral portion of the pressure receiving plate 61 at three positions in the circumferential direction so as to protrude outward in the radial direction in a claw shape.

The pressure receiving plate 61 is mounted on the main body base 23 by fitting the locking claws 61a from the right side to the corresponding locking portions 23d formed on the seat portion 23a of the main body base 23. They are connected in a state of being integrated in the direction of rotation. The pressure receiving plate 61 is interposed between the leaf spring 59 and the rotary ring 37, and the force partially pressed from the leaf spring 59 is widely dispersed in the in-plane direction and transmitted to the rotary ring 37. ing.

Next, the configuration of the control plate 56 will be described with reference to FIG. 9 and the like. The control plate 56 is composed of a member integrally having a double inner and outer ring plate shape whose surface faces in the seat width direction. In the control plate 56, the ring plate on the inner peripheral side and the ring plate on the outer peripheral side are connected to each other by connecting portions 56c at two points in the circumferential direction. The control plate 56 has a shape in which the ring plate on the inner peripheral side is offset to the left side of the ring plate on the outer peripheral side via the connecting portion 56c.

A central hole 56a is formed in the central portion of the control plate 56 (a portion through which the central axis C passes) so as to penetrate in a round hole shape in the axial direction. A cylindrical second shaft portion 22d forming an axially intermediate portion of the output shaft 22 is fitted into the center hole 56a so as to be rotatable (see FIGS. 7 to 8).

On the outer peripheral portion of the ring plate on the outer peripheral side of the control plate 56, insertion grooves recessed in a concave shape are formed at two positions in the circumferential direction thereof. Each of the corresponding arms 41c extending from the outer lever 41 described above is fitted into these insertion grooves from the right side. As a result, the control plate 56 is connected to the outer lever 41 in a state of being integrated in the rotational direction.

On the outer peripheral portion of the ring plate on the inner peripheral side of the control plate 56, hooking portions 56b are formed at four positions in the circumferential direction so as to extend outward in the radial direction in an arm shape. As shown in FIGS. 22 and 27, these hooking portions 56b are the inner circumferences of any of the corresponding pairs of the four poles 32 described above when the control plate 56 is turned in either direction. It is configured to be pressed against a surface and operated so as to disengage the rotating ring 37 from the internal gear 37a.

As shown in FIG. 9 and the like, on the outer peripheral portion of the ring plate on the outer peripheral side of the control plate 56, reliefs forming an arc-shaped outer peripheral surface drawn around the central axis C at three positions in the circumferential direction. A surface 56e and a riding surface 56f that is connected to the relief surface 56e and forms a concentric arcuate outer peripheral surface that is slightly larger than the relief surface 56e are formed. Each relief surface 56e and each climbing surface 56f have a shape in which their boundaries are connected by a gently sloping stepped surface.

As shown in FIG. 19, the control plate 56 is in a state in which the sliding portion 58b of each friction clutch 58 corresponding to each relief surface 56e is positioned when the inner lever 53 is in the neutral position. However, as shown in FIG. 21, the control plate 56 slides on each friction clutch 58 when the inner lever 53 is rotated from the neutral position in the clockwise direction (pushing down direction) shown in the drawing and is rotated integrally with the inner lever 53. The portion 58b is made to ride on each of the relief surfaces 56e corresponding to each of the climbing surfaces 56f. As a result, the control plate 56 pushes the sliding portion 58b of each friction clutch 58 outward in the radial direction.

On the other hand, as shown in FIG. 26, when the inner lever 53 is rotated in the counterclockwise direction (pulling direction) shown in the figure from the neutral position and is rotated integrally with the control plate 56, the friction clutch 58 slides. The portion 58b is slid along each of the corresponding relief surfaces 56e and held in a state of being positioned on each of the relief surfaces 56e. Therefore, in that case, the control plate 56 does not push the sliding portion 58b of each friction clutch 58 outward in the radial direction.

As shown in FIG. 9 and the like, the output shaft 22 has a pinion gear 22a, a first shaft portion 22b, a first spline 22c, a second shaft portion 22d, a second spline 22e, a third shaft portion 22f, and a fourth shaft portion from the left side. The configuration is such that 22 g are formed side by side on the same axis. The connection of each part of the output shaft 22 with other constituent members is as described above. The output shaft 22 is supported so that its second shaft portion 22d is fitted in the center hole 23c of the main body base 23 and is rotatable, and the fourth shaft portion 22g is fitted in the center hole 24a of the cover 24. It has a double-ended support structure that is supported so that it can rotate.

<About energy absorption unit E1>
By the way, as shown in FIG. 36, the rotation control device 18 further attaches a large load on the output shaft 22 to the connecting portion between the output shaft 22 and the planetary carrier 62 in the rotation direction from the sheet 1 side to a predetermined size or more. The configuration is provided with an energy absorbing unit E1 that plastically deforms when is input. Here, the planetary carrier 62 corresponds to the "power transmission unit" of the present invention.

Specifically, the energy absorbing portion E1 is formed in a fitting portion that is axially fitted to the output shaft 22 of the planetary carrier 62. More specifically, the energy absorbing portion E1 is deformed with the deformed portion D1 which is vulnerable to the force in the rotational direction by forming the lightening portion N1 in a part of the fitting portion of the planetary carrier 62. It is composed of a stop portion 62c that stops the deformation of the deformed portion D1 at a fixed position when the portion D1 is plastically deformed in the rotational direction.

Here, the internal gear-shaped spline hole 62a constituting the fitting portion of the planetary carrier 62 and the external gear-shaped first spline 22c of the output shaft 22 fitted in the spline hole 62a mesh with each other. The tooth shape is such that six uneven teeth are lined up in the direction of rotation. Then, the meat is formed so that each of the six internal teeth meshing between the external teeth of the first spline 22c of the planetary carrier 62 is recessed from the inner peripheral side to the outer peripheral side. A lightening portion N1 to be removed is formed.

Each lightening portion N1 is formed in an intermediate portion in the rotational direction of each corresponding internal tooth, that is, an intermediate portion in the rotational direction away from each abutting surface that abuts on each external tooth of the output shaft 22. As a result, both ends of the internal teeth thinned in the rotational direction by the lightening portions N1 are pressed in the rotational direction by the external teeth of the adjacent output shafts 22, so that they are easily plastically deformed. It is configured as a fragile deformed portion D1. Each deformed portion D1 is configured to project inward in the radial direction by the same length as the other internal teeth (stop portion 62c) in which the lightening portion N1 is not formed, and to be fitted between the external teeth of the output shaft 22. Will be done.

The stop portion 62c is formed by the internal teeth in which the lightening portion N1 is not formed, among the six internal teeth of the planet carrier 62 described above. With the above configuration, the food stop portion 62c has a structure having higher structural strength than the three internal teeth on which the deformed portion D1 is formed.

The first spline 22c of the output shaft 22 is set so that each external tooth is arranged as follows with respect to each internal tooth of the planetary carrier 62. That is, in the first spline 22c of the output shaft 22, among the internal teeth of the planetary carrier 62, each external tooth has a gap in the rotation direction with respect to the internal tooth (deformed portion D1) in which the lightening portion N1 is formed. It is set in a packed state. However, the first spline 22c of the output shaft 22 is set in a state in which a gap T is formed in the rotation direction with respect to the internal teeth in which the lightening portion N1 is not formed among the internal teeth of the planet carrier 62. Has been done.

With the above configuration, as shown in FIGS. 37 to 38, the output shaft 22 first receives the deformation portion D1 of the planetary carrier 62 and its rotation regardless of which rotation direction a large load is input from the sheet 1 side. Three external teeth adjacent to each other in the direction come into contact with each deformed portion D1 to apply a pressing force. Then, when the three external teeth of the output shaft 22 push and move each deformed portion D1 in the rotation direction to plastically deform the deformed portion D1, when the rotation progresses by the gap T, the other three external teeth are lightened. It is pressed in the rotational direction against another internal tooth (stop portion 62c) in which N1 is not formed.

As a result, the rotation of the output shaft 22 is strongly blocked by the other internal teeth (stop portion 62c) having a high structural strength in which the lightening portion N1 is not formed. Therefore, energy can be absorbed without excessively deforming the output shaft 22, and an excessive load input from the seat 1 side can be appropriately absorbed without significantly disturbing the posture of the seat 1.

<Summary>
Summarizing the above, the seat lifter device 10 according to the first embodiment has the following configuration. In the following, the reference numerals given in parentheses are the reference numerals corresponding to the respective configurations shown in the above embodiments.

That is, the seat lifter device (10) is a seat lifter device (10) provided with an output shaft (22) for raising and lowering the seat (1). The seat lifter device (10) includes a support portion (S) that supports the output shaft (22) so as to be rotatable, and a lock portion (B) that locks the rotation of the output shaft (22) with respect to the support portion (S). It has an energy absorbing portion (E1) provided in a power transmission path between the support portion (S) and the output shaft (22) via the lock portion (B).

The energy absorbing unit (E1) is plastically deformed when a large load in the rotation direction of a predetermined size or more is input from the sheet (1) side to the output shaft (22). According to the above configuration, the energy absorbing unit (E1) can appropriately absorb the excessive load input to the output shaft (22) from the sheet (1) side.

Further, the power transmission path is rotatably connected to the planetary carrier (62) integrally connected to the output shaft (22) and supported by the rotation of the output shaft (22). Locked with a plurality of planetary gears (63) that revolve while rotating along the internal gear (23e) formed in the portion (S), and a sun gear (38c) that meshes with the plurality of planetary gears (63) and rotates in conjunction with each other. It comprises a rotating member (38) whose rotation is locked by a portion (B) and a planetary gear mechanism (64) comprising. The energy absorbing portion (E1) is formed in a fitting portion that is axially fitted to the output shaft (22) of the planetary carrier (62).

According to the above configuration, even if the planetary gear mechanism (64) for accelerating the rotation of the output shaft (22) is provided, the speed is not increased between the output shaft (22) and the planetary carrier (62). Therefore, the excessive load input from the sheet (1) side to the output shaft (22) can be appropriately absorbed.

Further, the energy absorbing portion (E1) is plastically deformed with a deformed portion (D1) that is plastically deformed in the rotational direction when a large load in the rotational direction of a predetermined size or more is input to the output shaft (22). It has a pit portion (62c) having a higher structural strength than the deformed portion (D1) that stops the deformation of the deformed portion (D1) at a fixed position. According to the above configuration, while the deformed portion (D1) is appropriately deformed with the rotation of the output shaft (22), the stop portion (62c) can prevent the deformed portion (D1) from being excessively deformed. .. As a result, it is possible to appropriately absorb the excessive load input from the seat (1) side without significantly disturbing the posture of the seat (1).

Further, the output shaft (22) is provided in a state where the gap in the rotation direction is closed with respect to the deformed portion (D1). According to the above configuration, the deformed portion (D1) can be deformed from an early stage with the rotation of the output shaft (22), and the excessive load input from the seat (1) side can be absorbed more appropriately. can.

Further, the output shaft (22) is connected to the power transmission unit (62) forming the power transmission path by spline fitting. The deformed portion (D1) is located at an intermediate portion of the power transmission portion (62) that is separated from the contact surface between the tooth of the output shaft (22) and the tooth of the output shaft (22) of the tooth that abuts in the rotational direction in the rotational direction. By forming the lightening portion (N1), it has a fragile configuration in which it is plastically deformed in the rotational direction when a large load in the rotational direction of a predetermined size or more is input. According to the above configuration, the energy absorbing portion (E1) can be rationally and appropriately formed by using the configuration of the spline fitting portion of the output shaft (22) and the power transmission portion (62).

Further, the energy absorbing unit (E1) is configured to be plastically deformed by inputting a large load in the rotation direction having a predetermined size or more with respect to the bidirectional rotation of the output shaft (22) in the rotation direction. According to the above configuration, it is possible to appropriately absorb an excessive load in both rotation directions input from the sheet (1) side to the output shaft (22).

<< Second Embodiment >>
Subsequently, the configuration of the seat lifter device 10 according to the second embodiment of the present invention will be described with reference to FIG. 39. In the present embodiment, the rotation control device 19 has an electric type configuration in which the output shaft 73 is rotated in each direction by the rotation output of the electric motor 71 or is stopped by the braking force.

Specifically, the rotation control device 19 includes an electric motor 71, a housing 72, an output shaft 73, and a speed reducer 74. The housing 72 constitutes a support portion W that is integrally assembled with the right side frame 3a described above in FIG. 3 of the first embodiment. The output shaft 73 is assembled so as to be rotatable with respect to the housing 72.

The speed reducer 74 is configured to gear-connect the electric motor 71 and the output shaft 73 so that power can be transmitted. The speed reducer 74 includes a spur gear 74a which is composed of a gear train assembled to the housing 72 and is spline-fitted to the output shaft 73. The speed reducer 74 transmits the rotational output and braking force of the electric motor 71 from the spur gear 74a to the output shaft 73. That is, the electric motor 71 constitutes a lock portion P that locks the rotation of the output shaft 73 with respect to the support portion W.

The rotation control device 19 plastically deforms when a large load in the rotation direction of a predetermined size or more is input to the spline fitting portion between the spur gear 74a and the output shaft 73 from the seat 1 side. It is configured to include an energy absorbing unit E2. Here, the spur gear 74a corresponds to the "power transmission unit" of the present invention. The energy absorbing unit E2 has the same structure as the energy absorbing unit E1 described above in FIGS. 36 to 38 of the first embodiment.

That is, the spur gear 74a has a configuration corresponding to the planetary carrier 62 shown in FIGS. 36 to 38 of the first embodiment, and a large load in the rotation direction of a predetermined size or more is applied to the output shaft 73 from the sheet 1 side. When input, it is plastically deformed to absorb energy. Therefore, the description of the specific configuration of the energy absorbing unit E2 will be omitted.

<Summary>
Summarizing the above, the seat lifter device 10 according to the second embodiment has the following configuration. In the following, the reference numerals given in parentheses are the reference numerals corresponding to the respective configurations shown in the above embodiments.

That is, the seat lifter device (10) is a seat lifter device (10) provided with an output shaft (73) for raising and lowering the seat (1). The seat lifter device (10) includes a support portion (W) that supports the output shaft (73) so as to be rotatable, and a lock portion (P) that locks the rotation of the output shaft (73) with respect to the support portion (W). It has an energy absorbing portion (E2) provided in a power transmission path between a support portion (W) via a lock portion (P) and an output shaft (73).

The energy absorbing unit (E2) is plastically deformed when a large load in the rotation direction of a predetermined size or more is input from the sheet (1) side to the output shaft (73). According to the above configuration, the energy absorbing unit (E2) can appropriately absorb the excessive load input to the output shaft (73) from the sheet (1) side.

<< About other embodiments >>
Although the embodiments of the present invention have been described above using the two embodiments, the present invention can be implemented in various embodiments shown below in addition to the above embodiments.

1. 1. The seat lifter device of the present invention can be widely applied to seats mounted on vehicles other than automobiles such as railways, as well as seats mounted on vehicles other than vehicles such as aircraft and ships. Further, the seat lifter device can be widely applied to seats for non-vehicles such as bleachers and massage seats installed in various facilities such as sports facilities, theaters, concert venues, and event venues.

2. The energy absorbing unit may have another structure as shown in FIGS. 40 to 44 in addition to the structure shown in each of the above embodiments. In the energy absorbing portion E3 shown in FIG. 40, the lightening portion N2 formed on the specific internal teeth of the planetary carrier 62 (or the spur gear 74a (second embodiment)) has the entire area in the rotation direction of the specific internal teeth. It is formed over. With such a configuration, the deformed portion D2 thinned in the radial direction by the lightening portion N2 is rotated in the rotation direction from the outer teeth of the output shaft 22 (or the output shaft 73 (second embodiment)). It has a fragile configuration that is easily plastically deformed so that the diameter expands outward in the radial direction due to the pressing force. Since the configurations other than the above are the same as the configurations shown in the first embodiment, the same reference numerals are given and the description thereof will be omitted.

In the energy absorbing portion E4 shown in FIG. 41, the lightening portion N3 formed on the specific internal tooth of the planetary carrier 62 (or the spur gear 74a (second embodiment)) has the inner peripheral portion of the specific internal tooth and the internal peripheral portion of the specific internal tooth. The shape is such that the intermediate portion of the adjacent output shafts 22 (or the output shaft 73 (second embodiment)) that leaves the contact portion with each external tooth is hollowed out. With such a configuration, the deformed portion D3 thinned by the lightening portion N3 is pressed in the rotational direction from the outer teeth of the output shaft 22 (or the output shaft 73 (second embodiment)). The hollow shape of the lightening portion N3 is crushed by force in the radial direction and the rotational direction, resulting in a fragile structure that is easily plastically deformed. Since the configurations other than the above are the same as the configurations shown in the first embodiment, the same reference numerals are given and the description thereof will be omitted.

In the energy absorbing portion E5 shown in FIG. 42, the lightening portion N4 formed in the specific internal teeth of the planetary carrier 62 (or the spur gear 74a (second embodiment)) is intermediate in the rotation direction of the specific internal teeth. The portion is lightened so as to be recessed from the inner peripheral side to the outer peripheral side, and the both ends of the lightened portion in the rotational direction are cut in a slit shape to the outside in the radial direction. .. With such a configuration, the deformed portion D4 thinned by the lightening portion N4 is pressed in the rotational direction from the outer teeth of the output shaft 22 (or the output shaft 73 (second embodiment)). It has a fragile configuration that is easily plastically deformed so that it is tilted in the rotational direction with respect to the point deeply cut by the slit due to the force. Since the configurations other than the above are the same as the configurations shown in the first embodiment, the same reference numerals are given and the description thereof will be omitted.

The energy absorbing portion E6 shown in FIG. 43 has a lightening portion N5 formed on three specific internal teeth of the planetary carrier 62 (or spur gear 74a (second embodiment)), two of which are specific. One corner in the rotation direction of the internal teeth is lightened, and the remaining one is lightened in the other corner in the rotation direction of a specific internal tooth. With such a configuration, when the output shaft 22 (or the output shaft 73 (second embodiment)) receives a large load input from the seat side and is turned to one side and the other side. As a result, the easiness of deforming the deformed portion D5 weakened by the lightening portion N5 (rigidity of the deformed portion D5) can be changed.

Therefore, for example, the rigidity of the deformed portion D5 is made relatively high with respect to a large load input to the output shaft 22 (or the output shaft 73 (second embodiment)) due to the occurrence of a frontal collision of the vehicle. With respect to a large load input to the output shaft 22 (or the output shaft 73 (second embodiment)) due to the occurrence of a rear collision of the vehicle, the rigidity of the deformed portion D5 is changed to be relatively low. It becomes possible to make it. As a result, when a front collision of the vehicle occurs, the position of the occupant's physical restraint by the seat belt is hard to shift, and when a rear collision of the vehicle occurs, the energy absorbing unit E6 positively absorbs energy and the seat frame. It is possible to reduce the input load to the. Since the configurations other than the above are the same as the configurations shown in the first embodiment, the same reference numerals are given and the description thereof will be omitted.

In the energy absorbing portion E7 shown in FIG. 44, the lightening portion N6 formed in the specific internal teeth of the planetary carrier 62 (or the spur gear 74a (second embodiment)) is centered in the rotation direction of the specific internal teeth. It is formed at a position biased to one side of the portion. Even with such a configuration, the output shaft 22 (or the output shaft 73 (second embodiment)) receives a large load input from the seat side and is turned to one side and the other side. The easiness of deforming the deformed portion D6 weakened by the lightening portion N6 (rigidity of the deformed portion D6) can be changed.

3. 3. The energy absorbing portion may be provided in any power transmission path between the support portion and the output shaft via the lock portion. Further, the energy absorbing unit may be provided on either the output shaft or the power transmission unit spline-fitted to the output shaft, or may be provided on both. Further, the lightening portion constituting the energy absorbing portion may have a hole shape such as a circular shape or a triangular shape. Further, the energy absorbing unit may be provided so as to absorb energy only for a large load in either direction input from the seat side to the output shaft.

1 Seat 2 Seat back 3 Seat cushion 3a Side frame 3a 1 Through hole 4 Seat slide device 4a Lower rail 4b Upper rail 4c Leg 5 Operation handle 10 Seat lifter device 11 Link member 11a Sector gear 12 Section 4 Link mechanism 14 Support bracket 17 Torque rod 18 Rotation control device 19 Rotation control device 22 Output shaft 22a Pinion gear 22b 1st shaft 22c 1st spline 22d 2nd shaft 22e 2nd spline 22f 3rd shaft 22g 4th shaft 23 Main body base 23a Seat 23b Containment recess 23c Center hole 23d Locking part 23e Internal gear 24 Cover 24a Center hole 24b Engagement piece 24c Riding part 24d Seat part 24e Guide hole 24f Through hole 24g Through hole 24h Flange 24j Inclined surface 25 Intermediate base 25a Seat part 25b Shaft pin 25c Through hole 32 Pole 32a External tooth 32b Center hole 35 Torsion spring 36 Rotation transmission plate 36a Internal gear 36b Spline hole 37 Rotating ring 37a Internal gear 38 Rotating plate (rotating member)
38a Central hole 38b Meshing claw 38c Sun gear 41 Outer lever 41a Central hole 41b Through hole 41c Arm 43 Torsion spring 52 Feed claw 52a External tooth 52b Central hole 53 Inner lever 53a Central hole 53b Stopper pin 53c Through hole 53d Plate 56a Center hole 56b Hooking part 56c Connecting part 56e Escape surface 56f Riding surface 58 Friction clutch 58a Shaft pin 58b Sliding part 58c Inclined surface 59 Leaf spring 59a Locking claw 61 Pressure receiving plate 61a Locking claw 62 Planetary carrier (power Transmission part)
62a Spline hole 62b Shaft pin 62c Stop part 63 Planetary gear 63a Center hole 64 Planetary gear mechanism 71 Electric motor 72 Housing 73 Output shaft 74 Reducer 74a Spur gear (power transmission part)
S Support part W Support part A Feed part B Lock part P Lock part N Input part G Friction generation part U Acceleration part E1 to E7 Energy absorption part F Floor N1 to N6 Lightening part D1 to D6 Deformation part T Gap C Center axis

Claims (6)

A seat lifter device equipped with an output shaft that raises and lowers the seat.
A support portion that supports the output shaft so that it can rotate,
A lock portion that locks the rotation of the output shaft with respect to the support portion,
An energy absorbing portion provided in a power transmission path between the support portion and the output shaft via the lock portion, and a large load in the rotation direction of a predetermined size or more from the seat side with respect to the output shaft. A seat lifter device having the energy absorbing portion that is plastically deformed when is input. The seat lifter device according to claim 1.
The power transmission path is rotatably connected to a planetary carrier that is integrally connected to the output shaft, and is along an internal gear formed in the support portion as the output shaft rotates. It is composed of a planetary gear mechanism including a plurality of planetary gears that revolve while rotating, and a rotating member having a sun gear that meshes with the plurality of planetary gears and rotates in conjunction with the rotation, and whose rotation is locked by the lock portion.
A seat lifter device in which the energy absorbing portion is formed in a fitting portion that is axially fitted to the output shaft of the planet carrier. The seat lifter device according to claim 1 or 2.
The energy absorbing portion has a fixed position of a deformed portion that is plastically deformed in the rotational direction when a large load in the rotational direction of a predetermined size or more is input to the output shaft, and a deformed portion that is plastically deformed. A seat lifter device having a stop portion having a structural strength higher than that of the deformed portion. The seat lifter device according to claim 3.
A seat lifter device in which the output shaft is provided in a state where a gap in the rotation direction is closed with respect to the deformed portion. The seat lifter device according to claim 3 or 4.
The output shaft is connected to the power transmission unit forming the power transmission path by spline fitting.
A lightening portion is formed in an intermediate portion of the power transmission portion in which the deformed portion is in contact with the teeth of the output shaft in the rotational direction and is separated from the contact surface of the teeth of the output shaft in the rotational direction. A seat lifter device having a fragile structure that plastically deforms in the rotational direction when a large load in the rotational direction larger than the predetermined size is input. The seat lifter device according to any one of claims 1 to 5.
A seat lifter device in which the energy absorbing unit is plastically deformed by inputting a large load in the rotational direction having a predetermined size or more with respect to bidirectional rotation of the output shaft in the rotational direction.

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