JP7367598B2 - seat lifter device - Google Patents

Description

The present invention relates to a seat lifter device. Specifically, the present invention relates to a seat lifter device equipped with an output shaft that moves the seat up and down.

2. Description of the Related Art In a vehicle seat, a configuration is known that includes a seat lifter device that can adjust the seat height of a seat cushion (Patent Document 1). Specifically, the seat lifter device raises or lowers the seat height by a fixed amount by transmitting the amount of movement of the operation handle as the amount of rotational movement of a gear. It has become. When the operation handle is released, the seat lifter device locks the rotation of the gear at that position, and the operation handle is biased back to the neutral position before operation in an initial state where it can be operated again. It is now being returned to.

The feed rotation of the gear accompanying the operation of the operating handle is performed by pushing and moving a feed pawl meshed with the gear in the operating direction of the operating handle. Further, the gear rotation is locked as follows when the operation handle is released. In other words, a lock pawl consisting of a pair of symmetrical structures meshed with the above-mentioned gears is a ratchet-type lock pawl that is removed when the operating handle is operated, and the other one releases rotation in the feed direction but bites in the opposite direction. It has an interlocking structure, and when the operating handle is released, the other gear stops rotating at that position.

The feed pawl that feeds and rotates the gear is composed of a pair of symmetrical pawl structures, similar to the lock pawl, so that it can be returned to the neutral position when the operation handle is released. It has a ratchet-type meshing structure in which one side is removed from the gear when the operating handle is operated, and the other meshes with the gear so that power can be transmitted in the feeding direction, but rotation is released in the opposite direction.

JP2016-78850A

When an excessive load is applied to a vehicle seat due to a vehicle collision or the like, there is a possibility that the excessive load is transmitted from the seat lifter device held in a locked state to the seat frame. Therefore, the present invention provides a seat lifter device that can appropriately absorb 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 measures.

That is, the seat lifter device of the present invention is a seat lifter device including an output shaft that moves the seat up and down. This seat lifter device includes a support part that rotatably supports an output shaft, a lock part that locks rotation of the output shaft with respect to the support part, and a power transmission path between the support part and the output shaft via the lock part. and an energy absorbing section provided in the. The energy absorbing portion plastically deforms when a large load of a predetermined magnitude or more in the rotational direction is input to the output shaft from the seat side.

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

Moreover, the seat lifter device of the present invention may be further configured as follows. The power transmission path revolves around the planet carrier, which is integrally connected to the output shaft, and an internal gear that is rotatably connected to the planet carrier and is formed on the support part as the output shaft rotates. The planetary gear mechanism includes a plurality of planetary gears, and a rotating member that includes a sun gear that meshes with the plurality of planetary gears and rotates in conjunction with the planetary gears, and whose rotation is locked by a locking portion. An energy absorbing portion is formed in a fitting portion that is fitted in the output shaft of the planetary carrier in the axial direction.

According to the above configuration, even if a planetary gear mechanism is provided to speed up the rotation of the output shaft, excessive input to the output shaft from the seat side is generated between the output shaft that does not speed up and the planetary carrier. can absorb heavy loads appropriately.

Moreover, the seat lifter device of the present invention may be further configured as follows. The energy absorption part includes a deformation part that plastically deforms in the rotational direction when a large load of a predetermined magnitude or more in the rotational direction is input to the output shaft, and a deformation part that stops the deformation of the plastically deformed deformation part in a fixed position. It has a stopper part with higher structural strength than that of the conventional one.

According to the above configuration, while the deformable portion is appropriately deformed as the output shaft rotates, excessive deformation of the deformable portion can be prevented by the stopping portion. Thereby, an excessive load input from the seat side can be appropriately absorbed without significantly changing the posture of the seat.

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

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

Moreover, the seat lifter device of the present invention may be further configured as follows. The output shaft is connected to a power transmission section forming a power transmission path by spline fitting. The deformed portion is made to a predetermined size by forming a hollowed out portion in the middle portion in the rotational direction from the contact surface between the tooth of the output shaft of the power transmission portion and the tooth of the output shaft that contacts in the rotational direction. It has a weakened structure that plastically deforms in the rotational direction when a large load in the rotational direction is input.

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

Moreover, the seat lifter device of the present invention may be further configured as follows. The energy absorbing section is configured to plastically deform when a large load of a predetermined magnitude or more is applied to the output shaft in both directions of rotation.

According to the above configuration, it is possible to appropriately absorb excessive loads in both rotational directions that are input to the output shaft from the seat side.

FIG. 1 is an outer side view showing a schematic configuration of a seat lifter device according to a first embodiment. FIG. 3 is a side view of the structure on the outer surface side, viewed from inside in the seat width direction. FIG. 3 is an exploded perspective view showing a state in which the operating handle and the rotation control device are removed from the side frame of the seat cushion. FIG. 3 is a perspective view of the rotation control device viewed from the outside in the seat width direction. FIG. 3 is a perspective view of the rotation control device viewed from inside in the seat width direction. FIG. 3 is a front view of the rotation control device viewed from the outside in the seat width direction. 7 is a sectional view taken along the line VII-VII in FIG. 6. FIG. 7 is a sectional view taken along line VIII-VIII in FIG. 6. FIG. FIG. 3 is an exploded perspective view of the rotation control device viewed from the outside in the seat width direction. FIG. 9 is an exploded perspective view of FIG. 9 viewed from inside in the seat width direction. FIG. 2 is an exploded perspective view showing a state in which the components of the rotation control device are partially assembled. FIG. 12 is an exploded perspective view of FIG. 11 viewed from inside in the seat width direction. FIG. 3 is an exploded perspective view showing a state in which the component parts of the rotation control device are further assembled. FIG. 14 is an exploded perspective view of FIG. 13 viewed from inside in the seat width direction. FIG. 14 is an exploded perspective view showing a state in which the components of the rotation control device are partially assembled to a different assembly partner than those shown in FIG. 13; FIG. 16 is an exploded perspective view of FIG. 15 viewed from inside in the seat width direction. Furthermore, it is an exploded perspective view showing a state in which the component parts of the rotation control device are partially assembled. FIG. 18 is an exploded perspective view showing a state in which the components of the rotation control device are partially assembled to a different assembly partner than those shown in FIG. 17; FIG. 3 is a schematic diagram showing the state of the feed section when the operating handle is in the neutral position. FIG. 6 is a schematic diagram showing the state of the lock portion when the operating handle is in the neutral position. FIG. 6 is a schematic diagram showing the state of the feeding section when the operating handle is pushed down from the neutral position. FIG. 6 is a schematic diagram showing the state of the lock portion when the operating handle is pushed down from the neutral position. FIG. 7 is a schematic diagram showing the state of the lock portion when the operating handle is further pushed down. FIG. 6 is a schematic diagram showing the state of the sending section when the operating handle is returned to the neutral position. FIG. 6 is a schematic diagram showing the state of the lock portion when the operating handle is returned to the neutral position. FIG. 6 is a schematic diagram showing the state of the feed section when the operating handle is pulled up from the neutral position. FIG. 6 is a schematic diagram showing the state of the lock portion when the operating handle is pulled up from the neutral position. FIG. 7 is a schematic diagram showing the state of the lock portion when the operating handle is further pulled up. FIG. 3 is a schematic diagram showing the state of the sending section when the operating handle is returned to the neutral position. FIG. 6 is a schematic diagram showing the state of the lock portion when the operating handle is returned to the neutral position. FIG. 6 is a front view showing the state of the input section when the operating handle is in the neutral position. FIG. 7 is a front view showing the state of the input unit when the operating handle is pushed down to the maximum position. FIG. 7 is a front view showing the state of the input section when the operating handle is pulled up to the maximum position. FIG. 9 is an enlarged view of section XXXIV in FIG. 8 showing a friction suppressed state of the friction generating portion. FIG. 35 is an enlarged view corresponding to FIG. 34 showing a state in which the friction generating section is switched to a friction-on state. FIG. 3 is an enlarged view of a connecting portion between an output shaft and a planetary carrier. FIG. 37 is an enlarged view corresponding to FIG. 36 showing a state in which the planetary carrier is plastically deformed due to a large load being applied to the output shaft in the clockwise direction in the drawing; FIG. 37 is an enlarged view corresponding to FIG. 36 showing a state in which the planetary carrier is plastically deformed due to a large load being applied to the output shaft in the counterclockwise direction in the drawing; FIG. 2 is an exploded perspective view showing a schematic configuration of a seat lifter device according to a second embodiment. FIG. 7 is an enlarged view of main parts showing a schematic configuration of a seat lifter device according to another embodiment. FIG. 7 is an enlarged view of main parts showing a schematic configuration of a seat lifter device according to another embodiment. FIG. 7 is an enlarged view of main parts showing a schematic configuration of a seat lifter device according to another embodiment. FIG. 7 is an enlarged view of main parts showing a schematic configuration of a seat lifter device according to another embodiment. FIG. 7 is an enlarged view of main parts showing a schematic configuration of a seat lifter device according to another embodiment.

EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is demonstrated using drawing.

《First embodiment》
First, the configuration of a seat lifter device 10 according to a first embodiment of the present invention will be described using FIGS. 1 to 38. In the following description, when directions such as front, back, top, bottom, left, and right are indicated, the respective directions shown in each figure are referred to. In addition, when referring to "the sheet width direction", it refers to the left-right direction of the sheet 1, which will be described later.

<About the schematic configuration of the seat lifter device 10>
A seat lifter device 10 according to this embodiment is applied to a seat 1 of an automobile. As shown in FIGS. 1 and 2, the seat 1 includes a seat back 2 that serves as a backrest for a seated occupant, and a seat cushion 3 that serves 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 angle of the backrest 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 as to be able to adjust its position in the longitudinal direction.

Further, the seat cushion 3 is configured such that an electric seat lifter device 10 having a pair of left and right link structures is connected between the seat slide device 4 having the pair of left and right rail structures. By being connected via the seat lifter device 10, the seat cushion 3 can also be adjusted in position relative to the floor F in the height direction.

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

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. Due to the above connection, the seat lifter device 10 has a configuration including a pair of left and right four-bar link mechanisms 12 in which a pair of front and rear link members 11 respectively perform a link movement between the side frame 3a and the support bracket 14 on each side. be done.

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

The torque rod 17 is integrally bridged between the upper ends of the right rear link member 11 and the left rear link member 11, and drives and rotates both link members 11 synchronously. ing. When both the rear link members 11 move in unison, both the front link members 11 forming the four-bar link mechanism 12 also move synchronously. Thereby, 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 to the right side surface portion of the right side frame 3a. Specifically, the rotation control device 18 inserts the pinion gear 22a through a through hole 3a1 formed in the right side frame 3a and meshes with the sector gear 11a located on the left side of the side frame 3a. It is assembled into. As shown in FIG. 3, the rotation control device 18 is assembled with an operating handle 5 that extends forward.

The operating handle 5 is provided so as to extend forward from the rear right side of the seat cushion 3, and is configured to allow the user to raise and lower the seat cushion 3 from a neutral position. By raising and lowering the operating handle 5 from the neutral position, rotational forces in each operating direction are 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 right rear link member 11 is moved in the rotational direction corresponding to each operating direction.

Specifically, the rotation control device 18 is configured to maintain the operating handle 5 in a neutral position and to keep the output shaft 22 from rotating at all times before the operating handle 5 is operated. Ru. The rotation control device 18 outputs a rotational force to the pinion gear 22a in the direction of raising the right rear link member 11 forward when the operating handle 5 is operated to be pulled up from the neutral position. Thereby, the seat cushion 3 is pulled up from above the floor F.

Further, when the operating handle 5 is pressed down from the neutral position, the rotation control device 18 outputs a rotational force to the pinion gear 22a in the direction of tilting the right rear link member 11 rearward. . Thereby, the seat cushion 3 is pushed down onto the floor F. Further, the rotation control device 18 is configured to return the operating handle 5 to the neutral position while stopping the pinion gear 22a at the rotational position by releasing the operating state after the operating handle 5 is raised or lowered from the neutral position. It's supposed to work.

<About the schematic configuration of the rotation control device 18>
The specific configuration of the rotation control device 18 will be described below with reference to FIGS. 4 to 38. In the following description, any one of FIGS. 4 to 38 will be appropriately referred to for symbols that are not shown in the reference drawings among the members constituting the rotation control device 18. All members constituting the rotation control device 18 are made of pressed metal members.

As shown in FIGS. 4 to 8, the rotation control device 18 is constituted by a generally disc-shaped unit whose axis is oriented in the seat width direction. The rotation control device 18 has an input section N that is assembled integrally with the operating handle 5 shown in FIG. 3, and a support section S that is assembled integrally with the right side frame 3a.

The rotation control device 18 also includes an output shaft 22 that receives rotational force from the input section N, and a sending section A that transmits the rotational force from the input section N to the output shaft 22. Further, the rotation control device 18 has a lock section B that locks the rotation of the output shaft 22 when no rotational force is transmitted from the input section N, and a lock section B that increases the speed of the rotation of the output shaft 22. and a speed increasing part U that transmits the power to the power transmission path. Further, the rotation control device 18 includes a friction generating section G that applies a friction force to the rotation of the output shaft 22.

Specifically, as shown in FIGS. 9 to 18, the input section N is composed of a substantially disc-shaped outer lever 41 and an inner lever 53. These outer lever 41 and inner lever 53 are configured to be integrally assembled in line with each other on a central axis C extending in the seat width direction with a cover 24, which will be described later, in between.

The support portion S includes a main body base 23 having a substantially disk shape, an intermediate base 25 having a substantially ring plate shape, and a cover 24 having a substantially disk shape. The main body base 23, the intermediate base 25, and the cover 24 are arranged in order on a central axis C extending in the seat width direction and are integrally assembled.

The feeding section A is composed of four feeding claws 52 and a substantially disk-shaped rotation transmission plate 36. The four feed pawls 52 are each configured to be rotatably assembled to the aforementioned inner lever 53. The rotation transmission plate 36 is configured to be integrally assembled with the output shaft 22 inserted through its center portion (the portion through which the central axis C passes). Further, the rotation transmission plate 36 is arranged with the inner lever 53 on a central axis C extending in the seat width direction, and is assembled so as to be relatively rotatable 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 meshing the four feed pawls 52 with the internal gear 36a. Ru. As shown in FIGS. 21 and 26, when the inner lever 53 is rotated in either direction from the neutral position, the rotation transmission plate 36 is connected to a corresponding one of the four feed pawls 52 to be described later. is disengaged from engagement with the internal gear 36a, and is sent in the rotational direction of the inner lever 53 by engagement with the remaining pair.

Due to the above rotation, the rotation transmission plate 36 sends the output shaft 22, which is integrally assembled therewith, in the corresponding rotation direction. 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 in the rotationally operated position and moves only the inner lever 53 before the operation. can be returned to its initial position (neutral position). That is, as shown in FIGS. 21 and 26, when the inner lever 53 is turned in either direction from the neutral position, the rotation transmission plate 36 is fed in the rotational direction. Then, the rotation transmission plate 36 is temporarily locked at a position where the above-mentioned operation is stopped by the output shaft 22 being locked by a lock portion B described later.

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 operation, the rotation transmission plate 36 moves the pair of meshing feed pawls 52. By sliding it, only the inner lever 53 can be returned to the initial position before operation, together with each feed pawl 52, while leaving the inner lever 53 in the locked position.

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

The above-mentioned lock locks the rotation of the output shaft 22 which is gear-coupled with the rotating ring 37. As shown in FIGS. 22 and 27, when the aforementioned outer lever 41 is turned in either direction from the neutral position, the four pawls 32 are connected to one of the corresponding pairs via a control plate 56 (described later). is disengaged from the internal gear 37a of the rotating ring 37. As a result, the remaining pairs of the four poles 32 allow the rotating ring 37 to rotate in the corresponding direction, and as shown in FIGS. The state is such that rotation in the direction of rotation is allowed.

When the rotation of the operated outer lever 41 is returned, the four pawls 32 are arranged so that the pair of pawls 32 meshing with the internal gear 37a prevents the rotating ring 37 from rotating in the return direction. , holds the rotating ring 37 and the output shaft 22 in a locked state. Then, as shown in FIGS. 25 and 30, when the rotation of the outer lever 41 is returned, the remaining pairs of the four pawls 32 are returned to the state in which they are meshed with the internal gear 37a of the rotary ring 37. The rotation in both directions is locked.

As shown in FIGS. 9 to 18, the speed increasing unit 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. and a rotating plate 38 having a diameter of 38c. The planetary carrier 62 is configured to be integrally assembled with the output shaft 22 inserted through its center portion (the portion through which the central axis C passes). The three planet gears 63 are each configured to be rotatably assembled to the planet carrier 62. Here, the rotating plate 38 corresponds to the "rotating member" of the present invention.

The rotating plate 38 has the output shaft 22 inserted through its center (the part through which the central axis C passes), so that the sun gear 38c at the center is gear-coupled with the three planetary gears 63 so that power can be transmitted. It is said that the configuration is as follows. Further, the rotating plate 38 is configured such that its outer peripheral portion is fitted into the interior of the rotating ring 37 described above and assembled integrally.

The three connected planetary gears 63 are each set to be gear-connected to the internal gear 23e formed on the main body base 23 so as to be capable of transmitting power. As a result, the three planetary gears 63 rotate 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 in either direction from the neutral position. It has become. As the three planetary gears 63 rotate, the rotating plate 38 having the sun gear 38c gear-coupled to the center thereof is rotated in the same rotational direction as the output shaft 22.

At this time, the rotation plate 38 is rotated at an increased speed so as to rotate at a faster speed than the output shaft 22, depending on the gear ratio of each gear. The rotation causes the rotation plate 38 to rotate the rotation ring 37 integrally assembled therewith in the corresponding rotation direction. As described above, the rotation of the output shaft 22 is increased in speed by the speed increaser U and transmitted to the rotary ring 37, so that a frictional force is applied to the rotary ring 37 by the friction generating portion G to be described later, causing the rotary ring 37 to slip. The effect of preventing this can be effectively enhanced.

The friction generating section G includes three friction clutches 58, a plate spring 59 in the shape of a substantially wave washer, and a pressure receiving plate 61 in the shape of a substantially ring plate. The three friction clutches 58 are each configured to be assembled to the intermediate base 25 so as to be rotatable and movable in the axial direction.

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 in order on the inner surface (left side) of the cover 24, respectively. Specifically, the leaf spring 59 is set to be sandwiched between the pressure receiving plate 61 and the cover 24 in the axial direction. Further, the pressure receiving plate 61 is set so that the ring plate shapes thereof overlap in the axial direction with the rotating ring 37 described above. Further, the leaf spring 59 and the pressure receiving plate 61 are set such that their outer peripheral portions are engaged with the main body base 23 and are prevented from rotating.

The pressure receiving plate 61 is always subjected to an axial pressing force (resilient force) with the cover 24 as a fulcrum from the leaf spring 59 pressed between the plate spring 59 and the cover 24 . Thereby, the pressure receiving plate 61 is always held in a state where it is pressed against the rotating ring 37 in the axial direction (leftward direction). Due to the above pressing force, a frictional force is applied to the rotating ring 37 against its rotation.

As shown in FIG. 21, the three friction clutches 58 are operated by the control plate 56 in the radial direction when the control plate 56 is turned in the direction of pushing down the output shaft 22 (clockwise direction in the figure) by operating the outer lever 41. It is configured so that it is pushed out to the outside. As a result of the above extrusion, as shown in FIG. 35, the three friction clutches 58 ride on the inclined surfaces 24j formed on the cover 24, press the leaf springs 59 in the axial direction (leftward direction), and rotate. 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 that is integrally formed with an inner and outer ring plate shape. The control plate 56 is configured to be rotatably supported by the output shaft 22 by inserting the output shaft 22 through its center portion (the portion through which the central axis C passes). Further, the control plate 56 is configured to be integrally assembled with the outer lever 41 by fitting an arm 41c extending from the outer lever 41 into its outer peripheral portion.

As shown in FIGS. 21 and 26, the control plate 56 rotates integrally with the outer lever 41 when the outer lever 41 is turned in either direction from the neutral position, and the control plate 56 rotates integrally with the outer lever 41, and the four pawls 32 described above rotate. A corresponding one of the pairs is operated to disengage the internal gear 37a of the rotary ring 37. Furthermore, 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. When it is turned, the three friction clutches 58 are operated so as to be pushed outward in the radial direction.

Thereby, as shown in FIG. 35, the three friction clutches 58 press the leaf spring 59 in the axial direction (leftward direction) using the cover 24 as a fulcrum, thereby increasing the frictional force applied to the rotating ring 37. As described above, by applying a large frictional force to the rotation of the output shaft 22 in the direction in which it is pushed down, it is effective to prevent the output shaft 22 from slipping in the direction in which it is pushed down due to the action of its own weight applied to the seat 1, etc. can be suppressed.

As shown in FIGS. 9 to 18, the rotation control device 18 includes torsion springs 35, 43, and 55 in addition to the above. The torsion spring 35 is hooked between the aforementioned outer lever 41 and the cover 24, and is configured to urge the outer lever 41 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 pawls 52 described above, and biases each feed pawl 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 pawls 32 described above, and is configured to bias each pawl 32 in a rotational direction that meshes with the internal gear 37a of the rotating ring 37. .

<About the specific configuration of each part of the rotation control device 18>
Next, details of each member constituting the rotation control device 18 will be explained. First, the configurations of the outer lever 41 and the inner lever 53 that constitute the input section N will be explained with reference to FIG. 9 and the like. The outer lever 41 is made of a substantially disc-shaped member facing in the seat width direction. The aforementioned operating handle 5 is integrally assembled to the outer lever 41.

A center hole 41a is formed in the center portion of the outer lever 41 (the portion through which the center axis C passes) and extends through the center hole 41a in the shape of a circular hole in the axial direction. A cylindrical fourth shaft portion 22g forming the right side (outside in the seat width direction) end of the output shaft 22 is passed through the center hole 41a from the left side and rotatably fitted (see FIG. 7 ~See Figure 8). Furthermore, in the middle of the disc portion of the outer lever 41, a through hole 41b is formed at a symmetrical position in the circumferential direction and extends through the circular hole shape in the axial 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 coupled. Thereby, the outer lever 41 is integrally coupled with the inner lever 53.

Furthermore, arms 41c are formed on the peripheral edge of the outer lever 41 at two positions, upper and lower, to extend at right angles in the axial direction (leftward direction). These arms 41c are inserted from the right side into corresponding insertion grooves formed on the outer periphery of the control plate 56 through corresponding through holes 24g formed in the cover 24, which will be described later, and are integrally fitted. are combined. Thereby, the outer lever 41 rotates integrally with the control plate 56.

As shown in FIG. 9 and the like, the inner lever 53 is made of a substantially disc-shaped member facing in the seat width direction. A center hole 53a is formed in the center portion of the inner lever 53 (the portion through which the center axis C passes) and extends through the center hole 53a in the shape of a circular hole in the axial direction. The cylindrical third shaft portion 22f forming the axially intermediate portion of the output shaft 22 described above is inserted into the center hole 53a from the left side and rotatably fitted (see FIGS. 7 and 8). ).

Further, in the middle of the disk portion of the inner lever 53, a through hole 53c is formed in a symmetrical position in the circumferential direction and extends through the circular hole in the axial direction. A pair of stopper pins 53b are passed through the through holes 53c from the left side thereof and are integrally connected. Thereby, the inner lever 53 is integrally connected to the outer lever 41.

At the intermediate portion of the disk portion of the inner lever 53, shaft pins 53d are formed at four positions in the circumferential direction to project in the axial direction (rightward direction) in the shape of round pins. The four feed claws 52 described above are fitted into these shaft pins 53d from the right side and rotatably connected.

Next, the configurations of the main body base 23, intermediate base 25, and cover 24 that constitute the support section S will be explained with reference to FIG. 9 and the like. The main body base 23 is made of a substantially disk-shaped member facing in the seat width direction. An internal gear 23e is formed in the center of the main body base 23 and is semi-hollowed into a substantially cylindrical shape extruded in the axial direction (rightward direction).

On the inner circumferential surface of the internal gear 23e, internal teeth are formed in an endless shape over the entire circumference, with which the three planetary gears 63 described above can mesh with each other so as to transmit power. A central hole 23c is formed in the center of the internal gear 23e of the main body base 23 (the part through which the central axis C passes), and extends through the internal gear 23e in the axial direction. A pinion gear 22a formed at the left end (inner side in the seat width direction) of the output shaft 22 is passed through the center hole 23c from the right side (outer side in the seat width direction), and is passed through the center hole 23c at the axial center of the output shaft 22. A cylindrical first shaft portion 22b forming a portion is rotatably fitted (see FIGS. 7 and 8).

Through the above assembly, the output shaft 22 and the aforementioned planetary carrier 62 and three planetary gears 63 that are assembled thereto are set in the housing recess 23b that forms the area within the internal gear 23e of the main body base 23, respectively. Ru. Specifically, the three planetary gears 63 are set to mesh with the internal gear 23e of the main body base 23 so as to be capable of transmitting power.

As shown in FIG. 9, etc., a seat portion 23a is formed in a portion of the main body base 23 projecting from the periphery of the internal gear 23e, and the seat portion 23a is set in such a manner that the aforementioned rotating ring 37 is applied in the axial direction. . At three locations around the seat portion 23a, locking claws 59a and 61a protruding from the three corresponding locations of the leaf spring 59 and pressure receiving plate 61 described above are fitted in the axial direction so as to be integrated in the rotational direction. A locking portion 23d is formed that can be locked in the state.

The main body base 23 has the above-mentioned intermediate base 25 and cover 24 set in a portion protruding from the periphery of the internal gear 23e so as to be stacked one on top of the other in the axial direction from the right side (outside in the seat width direction). They are integrally connected by bolts (not shown). The main body base 23 is also integrally connected to the aforementioned right side frame 3a by bolting (not shown).

The intermediate base 25 is made of a substantially ring plate-shaped member facing in the seat width direction. In the intermediate base 25, shaft pins 25b projecting in the axial direction (leftward direction) in the shape of round pins are formed at four positions in the circumferential direction of the seat portion 25a forming a ring plate shape. The four poles 32 described above are fitted into these shaft pins 25b from the left side and are rotatably connected.

In addition, the intermediate base 25 is formed with through holes 25c that penetrate in the axial direction in the shape of round holes at three positions in the circumferential direction of the seat portion 25a. Shaft pins 58a projecting in the axial direction (rightward direction) in the shape of round pins of the three friction clutches 58 described above are respectively fitted into these through holes 25c from the left side and are rotatably connected.

The cover 24 is made of a substantially disc-shaped member facing in the seat width direction. The cover 24 is formed with a flange 24h that extends from its outer peripheral edge in a substantially cylindrical shape in the axial direction (leftward direction). The cover 24 has a seat portion 24d that is bent at right angles to the outer circumferential side at two points at the protruding end of the flange 24h, and these seat portions 24d are placed around the body base 23 mentioned above and bolted ( (not shown) so that it is integrally coupled with the cover 24. By the above-mentioned connection, the cover 24 is set in a state in which the components such as the feed section A and the lock section B are enclosed between the cover 24 and the main body base 23 (see FIGS. 4 and 5).

Further, as shown in FIG. 9 and the like, a center hole 24a is formed in the center of the disc of the cover 24 (the part through which the center axis C passes), which penetrates in the axial direction in a circular hole shape. A cylindrical fourth shaft portion 22g forming the right side (outside in the seat width direction) end of the output shaft 22 is passed through the center hole 24a from the left side and rotatably fitted (see FIG. 7 ~See Figure 8).

Further, as shown in FIG. 9 and the like, an engaging piece 24b is formed on the peripheral edge of the disc portion of the cover 24 and is cut and raised at right angles in a shape that extends in the axial direction (rightward direction). One of the pair of arms 41c protruding from the peripheral edge of the outer lever 41 is set on the engagement piece 24b so as to be stacked on the inside in the radial direction.

Each end of the torsion spring 35 is hooked between the arm 41c and the engagement piece 24b. Due to the engagement of the torsion spring 35, the outer lever 41 is always biased so that the circumferential arrangement of the arm 41c and the engagement piece 24b coincides with each other, and is held at a neutral position with respect to the cover 24.

As shown in FIG. 10, etc., a run-up portion 24c is formed on the peripheral edge of the disc portion of the cover 24, and is cut and raised at right angles in a shape extending in the axial direction (leftward direction) from a symmetrical position in the circumferential direction. There is. As shown in FIG. 19, these riding portions 24c are set 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 formed on the upper left side and 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 direction in the figure). The two feed pawls 52 are placed against their edges to disengage the two feed pawls 52 from the internal gear 36a of the rotation transmission plate 36. Further, as shown in FIG. 24, each riding portion 24c allows the two feed pawls 52 that have been disengaged to mesh with the internal gear 36a of the rotation transmission plate 36 when the inner lever 53 is turned back. return to the original state.

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

As shown in FIG. 10, etc., a guide hole 24e extending in the shape of an arc drawn around the central axis C and penetrating in the axial direction is formed in the middle part of the disc part of the cover 24 at a symmetrical position in the circumferential direction. It is formed. Each of the stopper pins 53b, which are passed through the aforementioned outer lever 41 and the inner lever 53 in the axial direction, are passed through the guide holes 24e from the left side, respectively.

Each of the guide holes 24e has an arcuate shape that allows the outer lever 41 and the inner lever 53 to be pushed down (see FIG. 32) or pulled up (see FIG. 33) from the neutral position (see FIG. 31) as a unit. (see). Each guide hole 24e is configured to lock the raising and lowering operations of the outer lever 41 and the inner lever 53 at respective positions where each stopper pin 53b hits the end of the hole extending in an arc shape (Figs. 32 to 32). 33).

As shown in FIG. 9 and the like, through holes 24f are formed in the circumferential edge of the disk portion of the cover 24 at three positions in the circumferential direction, and pass through in the axial direction in the shape of a circular hole. These through-holes 24f are configured such that shaft pins 58a projecting in the axial direction (rightward direction) in the shape of round pins from the three friction clutches 58 described above can be passed through from the left side.

As shown in FIG. 10, etc., the peripheral edge of the disc portion of the cover 24 has through holes 24g extending in an arc shape drawn around the central axis C in the axial direction at two positions above and below. It is formed. One of the upper through holes 24g is formed in an overlapping position communicating with the cut and raised hole of the above-mentioned engagement piece 24b.

Each corresponding arm 41c extending in the axial direction (leftward direction) from the peripheral edge of the outer lever 41 described above is passed through each through hole 24g from the right side. Thereby, each through hole 24g allows movement of each arm 41c to escape when the outer lever 41 is rotated from the neutral position.

Next, the configurations of the four feed claws 52 and the rotation transmission plate 36 that constitute the feed section A will be described with reference to FIG. 9 and the like. The four feed claws 52 each consist of an arm-shaped member facing in the sheet width direction. Each of the feed claws 52 has a center hole 52b formed at its base end and passing through in the axial direction in a circular hole shape, and is fitted from the right side into each corresponding shaft pin 53d formed on the inner lever 53 described above. and are rotatably connected.

As shown in FIG. 19, the four feed pawls 52 are arranged in pairs with respect to the inner lever 53 in the front and back, and the top and bottom, respectively. Of the 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 an arm extends in the counterclockwise direction in the figure from the respective rotation center (axis pin 53d). Further, the remaining two feeding claws 52 on the lower front side and the upper rear side each have a shape in which an arm extends in the clockwise direction in the figure from the respective rotation center (axis pin 53d).

The four feed pawls 52 have external teeth 52a formed at the tips of their arms that can mesh with the internal gear 36a of the rotation transmission plate 36. A torsion spring 43 is hooked between each of the front and rear pairs of the four feed claws 52, respectively. Each torsion spring 43 is set in such a manner that its central coiled portion is passed through each stopper pin 53b that is passed through the inner lever 53.

The upper torsion spring 43 is set in such a state that one end and the other end thereof are pressed in a biasing direction that exerts an elastic force on the upper front feeding claw 52 and the upper rear feeding claw 52, respectively. ing. The lower torsion spring 43 is in a state in which its one end and the other end are pressed in a biasing direction that exerts an elastic force on the lower front feeding claw 52 and the lower rear feeding claw 52, respectively. is set to .

Due to the biasing force of each torsion spring 43, each feed pawl 52 is normally pushed outward in the radial direction around its respective rotation center (axis pin 53d), as shown in FIG. The external teeth 52a are held in mesh with the internal gear 36a of the rotation transmission plate 36. The four feed pawls 52 have a meshing force that their external teeth 52a exert on the internal gear 36a of the rotation transmission plate 36. The three feeding claws 52 have different configurations from each other.

Specifically, when the external teeth 52a of the two feeding pawls 52 on the front upper side and the rear lower side mesh with the internal gear 36a, the inner lever 53 moves from the neutral position in the clockwise direction as shown in FIG. By being turned in the (pushing down direction), the internal gear 36a is configured to mesh integrally in the rotational direction so that the internal gear 36a can be pushed in that direction. However, the two feeding claws 52 on the front upper side and the rear lower side cannot be used against the rotation of the inner lever 53, which is returned to the initial position before operation, as shown in FIG. 24, after being turned clockwise in the figure. , and is not integrated with the internal gear 36a, but is returned to the initial position before operation while sliding on the internal gear 36a in the rotational direction.

On the other hand, returning to FIG. 19, when the outer teeth 52a of the two feed pawls 52 on the rear upper side and the front lower side mesh with the internal gear 36a, the inner lever 53 is moved from the neutral position to the position shown in FIG. When turned counterclockwise (pulling direction), the internal gear 36a is meshed integrally in the rotational direction so that the internal gear 36a can be pushed in that direction. However, the two feed claws 52 on the rear upper side and the front lower side are not able to handle the rotation of the inner lever 53 after it is turned counterclockwise in the figure and returned to the initial position before operation, as shown in FIG. 29. is not integrated with the internal gear 36a, but is returned to the initial position before operation while sliding on the internal gear 36a in the rotational direction.

With the above configuration, the four feeding pawls 52 can push and turn the rotation transmission plate 36 in whichever direction the inner lever 53 is turned from the neutral position. When the inner lever 53 is returned to the neutral position from the rotated position in each direction, the four feed pawls 52 leave the rotation transmission plate 36 in the rotated position and return the inner lever 53 to the initial position before operation. It is now possible to return it.

As shown in FIG. 21, when the inner lever 53 is turned in the clockwise direction (pushing down direction) in the drawing from the neutral position, the four feeding claws 52 on the rear upper side and the front lower side move. It is disengaged from the internal gear 36a and held in that state. Further, as shown in FIG. 26, when the inner lever 53 is turned from the neutral position in the counterclockwise direction (in the drawing direction), the two feed pawls 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 rotated position in each direction to the neutral position, the two feed pawls 52 act to restrict the movement of the inner lever 53. It is designed so as not to impede the return movement. Specifically, as shown in FIG. 21, when the inner lever 53 is turned from the neutral position in the clockwise direction (pushing down direction) in the figure, the two feed claws 52 on the rear upper side and the front lower side move the cover as described above. 24, and is rotated so as to be disengaged from the internal gear 36a. Then, while the inner lever 53 is operated in the above direction, the two feeding pawls 52 on the rear upper side and the front lower side are in a state of riding on each of the riding parts 24c, and are prevented from meshing with the internal gear 36a. It is kept 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 (in the drawing direction), the two feed claws 52 on the front upper side and the rear lower side move the cover 24 as described above. It is pressed against the edge of each riding portion 24c and turned so as to be disengaged from the internal gear 36a. While the inner lever 53 is operated in the above direction, the two feeding pawls 52 on the front upper side and the rear lower side are in a state of riding on each riding portion 24c, and are prevented from meshing with the internal gear 36a. It is kept in the removed state.

Returning to FIG. 19, the two feed pawls 52 on the rear upper side and the front lower side are arranged so that their external teeth 52a mesh with the teeth of the internal gear 36a at positions shifted by a half pitch from each other. There is. Similarly, the two feed pawls 52 on the front upper side and the rear lower side are arranged so that their external teeth 52a mesh with the teeth of the internal gear 36a at positions shifted by half a pitch from each other. With this configuration, play in the rotational direction that may occur between the external teeth 52a of each feed pawl 52 and the internal gear 36a when they mesh with each other is suppressed to a minimum.

The rotation transmission plate 36 is made of a substantially disk-shaped member facing in the seat width direction. An internal gear 36a is formed in the center of the rotation transmission plate 36, and is half-hollowed into a substantially cylindrical shape extruded in the axial direction (rightward direction). An internal gear-shaped spline hole 36b that penetrates in the axial direction is formed in the center of the disc of the rotation transmission plate 36 (the part through which the central axis C passes).

An external gear-shaped second spline 22e forming an axially intermediate portion of the output shaft 22 is inserted into the spline hole 36b from the left side and is fitted into the spline hole 36b so as to be integral with the spline hole 36b in the rotational direction. Due to the above fitting, the rotation transmission plate 36 is connected integrally with the output shaft 22 in the rotational direction.

Next, the configuration of the four poles 32 and the rotating ring 37 that constitute the lock portion B will be described with reference to FIG. 9 and the like. The four poles 32 each consist of an arm-shaped member facing in the seat width direction. Each pole 32 has a center hole 32b formed at its base end and passing through in the axial direction in a circular hole shape, and is fitted from the left side into each corresponding shaft pin 25b formed in the intermediate base 25 described above. and are rotatably connected.

As shown in FIG. 20, the four poles 32 are arranged in pairs on the intermediate base 25, front and rear, and upper and lower, respectively. Of the four poles 32, the two poles 32 on the front upper side and the rear lower side each have a shape in which an arm extends in the counterclockwise direction in the figure from the respective rotation center (axis pin 25b). Further, the remaining two poles 32 on the lower front side and the upper rear side each have a shape in which arms extend clockwise in the figure from their respective rotation centers (axis pins 25b).

The four pawls 32 have external teeth 32a formed at the tips of their arms that can mesh with the internal gear 37a of the rotating ring 37. A torsion spring 55 is hooked between each upper and lower pair of the four poles 32, respectively.

Specifically, the front torsion spring 55 is set such that one end and the other end thereof are applied in a biasing direction that exerts an elastic force on the front upper pole 32 and the front lower pole 32, respectively. has been done. Further, the torsion spring 55 on the rear side is set in such a state that its one end and the other end are applied in the biasing direction to exert an elastic force on the upper rear pole 32 and the lower rear pole 32, respectively. There is.

Due to the biasing force of each torsion spring 55, each pole 32 is normally pushed outward in the radial direction around its respective rotation center (axis pin 25b), as shown in FIG. The teeth 32a are held in mesh with the internal gear 37a of the rotating ring 37. The above-mentioned four pawls 32 have two pawls 32 on the front upper side and a rear lower side, and two pawls 32 on the front lower side and a rear upper side. and have different configurations.

Specifically, the two pawls 32 on the front upper side and the rear lower side prevent the rotating ring 37 from rotating in the clockwise direction (pushing down direction) in the figure by having their external teeth 32a mesh with the internal gear 37a. It is considered to be a composition. However, even if the external teeth 32a of the two pawls 32 on the front upper side and the rear lower side mesh with the internal gear 37a, as shown in FIG. ), it is configured to slide on the internal gear 37a and release the rotation of the rotary ring 37.

On the other hand, returning to FIG. 20, the two poles 32 on the rear upper side and the front lower side have their external teeth 32a meshing with the internal gear 37a, so that the rotation ring 37 moves counterclockwise (in the pulling direction) as shown in the figure. It is configured to prevent rotation. However, even if the external teeth 32a of the two pawls 32 on the rear upper side and the front lower side mesh with the internal gear 37a, as shown in FIG. When the rotary ring 37 is rotated, it slides on the internal gear 37a to release the rotation of the rotary ring 37.

The four poles 32 are brought into the following state by turning the inner lever 53 from the neutral position in the clockwise direction (in the downward direction) as shown in FIG. 21. That is, as shown in FIG. 22, due to the above rotation, the two poles 32 on the front upper side and the rear lower side are disengaged from the internal gear 37a by the control plate 56 and held in that state. On the other hand, the two pawls 32 on the rear upper side and the front lower side remain in mesh with the internal gear 37a. As a result, the four pawls 32 are in a state in which they can release the rotation of the rotating ring 37 in the clockwise direction (pushing down direction) in the drawing (see FIG. 23).

When the inner lever 53 is returned to the neutral position as shown in FIG. 24 after the rotary ring 37 is rotated clockwise in the drawing, the four pawls 32 are located at the rear upper side that meshes with the internal gear 37a. The two pawls 32 on the front and lower sides prevent the rotating ring 37 from rotating in the counterclockwise direction shown in the figure, and hold the rotating ring 37 in a fixed position (see FIG. 25). Then, by returning the operation of the inner lever 53 (see FIG. 24), 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 rotated 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 enter the following state by turning the inner lever 53 from the neutral position in the counterclockwise direction (in the pulling direction) as shown in FIG. 26. That is, as shown in FIG. 27, due to the above rotation, the two poles 32 on the rear upper side and the front lower side are disengaged from the internal gear 37a by the control plate 56 and held in that state. On the other hand, the two pawls 32 on the front upper side and the rear lower side remain in mesh with the internal gear 37a. Thereby, the four poles 32 are in a state where they can release the rotation of the rotating ring 37 in the counterclockwise direction (in the pulling direction) as shown in the figure (see FIG. 28).

When the inner lever 53 is returned to the neutral position as shown in FIG. 29 after the rotation ring 37 is rotated in the counterclockwise direction shown in the figure, the four pawls 32 are in the front position engaged with the internal gear 37a. The two upper and lower rear poles 32 prevent rotation of the rotary ring 37 in the clockwise direction shown and hold the rotary ring 37 in place (see FIG. 30). Then, by returning the operation of the inner lever 53 (see FIG. 29), 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 rotated, 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 made of a substantially ring plate-shaped member whose surface faces in the seat width direction. The rotary ring 37 has an internal gear 37a formed on the inner periphery of the ring plate and projecting in a substantially cylindrical shape in the axial direction (rightward direction). On the inner circumferential surface of the internal gear 37a, internal teeth are formed in an endless shape over the entire circumference, with which the external teeth 32a of the four pawls 32 described above can be engaged. The rotating ring 37 is set such 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 carrier 62, three planetary gears 63, and rotating plate 38 that constitute the speed increasing section U will be explained with reference to FIG. 9 and the like. The planet carrier 62 is made of a substantially disk-shaped member facing in the seat width direction. An internal gear-shaped spline hole 62a is formed in the center of the planetary carrier 62 (the part through which the central axis C passes) and passes through the planetary carrier 62 in the axial direction.

An external gear-shaped first spline 22c forming an axially intermediate portion of the output shaft 22 is inserted into the spline hole 62a from the left side and is fitted into the spline hole 62a so as to be integral with the spline hole 62a in the rotational direction. Due to the above fitting, the planet carrier 62 is connected integrally with the output shaft 22 in the rotational direction.

The planet carrier 62 is provided with shaft pins 62b that protrude in the axial direction (rightward direction) in the shape of round pins at three circumferential positions on the ring plate. Three planetary gears 63, which will be described later, are fitted into these shaft pins 62b from the right side and rotatably connected.

The three planetary gears 63 are each configured as a disc-shaped external gear facing in the seat width direction. The three planetary gears 63 are rotatable by having a center hole 63a formed in the center thereof and penetrating in the axial direction in a circular hole shape fitted into each corresponding shaft pin 62b of the planetary carrier 62 from the right side. are connected like this.

The three planetary gears 63 are assembled to the main body base 23 via the planetary carrier 62 and the output shaft 22, and are set to mesh with the internal gear 23e of the main body base 23 (see FIG. 13, etc.). With the above assembly, the three planetary gears 63 are configured to rotate and revolve along the internal gears 23e of the main body base 23 when the output shaft 22 is rotated in either direction.

As shown in FIG. 9 and the like, the rotating plate 38 is made of a substantially disc-shaped member facing in the seat width direction. A central hole 38a is formed in the center of the rotary plate 38 (the portion through which the central axis C passes) and extends through the rotary plate 38 in the axial direction. A cylindrical second shaft portion 22d forming an axially intermediate portion of the output shaft 22 is rotatably fitted into the center hole 38a (see FIGS. 7 and 8).

Further, as shown in FIG. 10 and the like, a sun gear 38c is formed in the center of the rotary plate 38 and protrudes in the axial direction from around the center hole 38a. By setting the output shaft 22 in the center hole 38a, the sun gear 38c is set between the three planetary gears 63 mentioned above, and is gear-coupled with each planetary gear 63 so that power can be transmitted. .

Thereby, the three planetary gears 63 rotate with the rotation of the output shaft 22, and the sun gear 38c rotates by receiving the rotational driving force transmitted therefrom. Specifically, the sun gear 38c rotates by increasing the speed at which the three planetary gears 63 rotate inside the internal gear 23e of the main body base 23 according to the meshing gear ratio.

On the outer periphery of the rotating plate 38, engaging pawls 38b that can engage with the internal gear 37a of the rotating ring 37 are formed at a plurality of locations in the circumferential direction. The rotating plate 38 is set in the internal gear 37a of the rotating ring 37 so that the engaging claws 38b mesh with the internal gear 37a of the rotating ring 37. Thereby, the rotating plate 38 is connected integrally with the rotating ring 37 in the rotational direction. With the above configuration, the rotary plate 38 rotates the sun gear 38c at the center as the output shaft 22 rotates, thereby rotating the rotary ring 37 at an increased rotational speed.

Next, the configuration of the three friction clutches 58, leaf spring 59, and pressure receiving plate 61 that constitute the friction generating section G will be explained with reference to FIG. 9 and the like. The three friction clutches 58 each consist of an arm-shaped member facing in the seat width direction. At the base end of each friction clutch 58, a shaft pin 58a is formed which projects in the axial direction (rightward direction) in the shape of a round pin. Each shaft pin 58a is passed from the left side into a corresponding through hole 25c formed in the intermediate base 25 described above, and is engaged therewith so as to be rotatable and movable in the axial direction.

The three friction clutches 58 have sliding portions 58b formed at the tips of their arms that bulge in the axial direction (rightward direction) and come into surface contact with the inner surface (left side) of the cover 24. As shown in FIG. 34, each sliding portion 58b is normally in contact with the inner (left side) general surface of the cover 24. As shown in FIG. However, as described above with reference to FIG. 21, each sliding portion 58b is rotated from the inside in the radial direction to the outside by the control plate 56 when the inner lever 53 is turned from the neutral position in the clockwise direction (pushing down direction) in the figure. Pressed.

As a result, each friction clutch 58 is pushed radially outward around its center of rotation (axis pin 58a), and as shown in FIG. (The left side surface) is made to ride on each corresponding inclined surface 24j formed at three positions in the circumferential direction. Specifically, each friction clutch 58 has each chamfered inclined surface 58c formed on the outer peripheral area on the right side surface of each sliding portion 58b along the corresponding inclined surface 24j of the cover 24. Let them ride on the vehicle while they are in contact with each other.

As a result, each sliding portion 58b is pushed outward in the radial direction along each inclined surface 24j of the cover 24 and moved to the left. Due to the above-mentioned diagonal movement, each sliding portion 58b pushes the wavy portion of the leaf spring 59 that contacts the sliding portion 58b from the left side toward the right side.

By the above-mentioned pushing, each sliding portion 58b exerts a force to press the pressure receiving plate 61 to the left side through the elastic force of the leaf spring 59, and slides due to the rotation of the rotary ring 37 whose surface is in contact with the pressure receiving plate 61 from the left side. Apply dynamic friction resistance force. 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 (in the pulling direction) as shown in FIG. As shown in 34, the cover 24 remains in contact with the inner (left side) general surface.

As shown in FIG. 9 and the like, the leaf spring 59 is made of a substantially wave washer-like member whose surface faces in the sheet width direction. On the outer circumferential portion of the leaf spring 59, locking claws 59a that protrude outward in the radial direction are formed at three positions in the circumferential direction. The plate spring 59 is fixed to the main body base 23 by fitting the locking claws 59a from the right side into the corresponding locking parts 23d formed on the seat 23a of the main body base 23. and are connected in a state where they become integral in the rotational direction.

The leaf spring 59 is configured to constantly apply a constant elastic force in the axial direction between the pressure receiving plate 61 and each friction clutch 58 due to its undulating shape. The leaf spring 59 is switched so as to strengthen the elastic force acting on the pressure receiving plate 61 when each friction clutch 58 is pushed outward in the radial direction and pressed from the right side as described above with reference to FIG. The configuration is as follows.

As shown in FIG. 9 and the like, the pressure receiving plate 61 is made of a substantially ring plate-shaped member whose surface faces in the seat width direction. On the outer circumferential portion of the pressure receiving plate 61, similarly to the leaf spring 59, locking claws 61a that protrude outward in the radial direction are formed at three positions in the circumferential direction.

The pressure receiving plate 61 is fixed to the main body base 23 by fitting the locking claws 61a from the right side into the corresponding locking parts 23d formed on the seat 23a of the main body base 23. and are connected in a state where they become integral in the rotational direction. The pressure receiving plate 61 is interposed between the leaf spring 59 and the rotary ring 37, and transmits the force partially pressed by the leaf spring 59 to the rotary ring 37 while widely distributing it in the in-plane direction. ing.

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

A central hole 56a is formed in the central portion of the control plate 56 (the portion through which the central axis C passes) and extends through the control plate 56 in the shape of a circular hole in the axial direction. A cylindrical second shaft portion 22d forming an axially intermediate portion of the output shaft 22 is rotatably fitted into the center hole 56a (see FIGS. 7 and 8).

Concave insertion grooves are formed on the outer circumference of the ring plate on the outer circumference side of the control plate 56 at two positions in the circumferential direction. Each corresponding arm 41c extending from the aforementioned outer lever 41 is fitted into these insertion grooves from the right side. Thereby, the control plate 56 is connected integrally with the outer lever 41 in the rotational direction.

On the outer circumferential portion of the ring plate on the inner circumferential side of the control plate 56, hook portions 56b extending radially outward in the shape of arms are formed at four positions in the circumferential direction. As shown in FIGS. 22 and 27, when the control plate 56 is turned in either direction, these hook portions 56b are attached to the inner periphery of a corresponding pair of the four poles 32. It is configured to be pressed against a surface and manipulated to disengage them from the internal gear 37a of the rotating ring 37.

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

As shown in FIG. 19, when the inner lever 53 is in the neutral position, the control plate 56 positions the corresponding sliding portion 58b of each friction clutch 58 on each relief surface 56e. However, as shown in FIG. 21, the control plate 56 controls the sliding of each friction clutch 58 by turning the inner lever 53 from the neutral position in the clockwise direction (pushing down direction) in the drawing and turning it integrally with the inner lever 53. The portion 58b is made to ride on each rising surface 56f from the corresponding relief surface 56e. Thereby, the control plate 56 pushes the sliding portion 58b of each friction clutch 58 radially outward.

On the other hand, as shown in FIG. 26, when the inner lever 53 is turned from the neutral position in the counterclockwise direction (in the direction of pulling up) as shown in the figure and is rotated integrally with the inner lever 53, the control plate 56 controls the sliding of each friction clutch 58. The portion 58b is slid along each corresponding relief surface 56e and held on each relief surface 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 etc., the output shaft 22 includes, from the left side, 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. 22g 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 has a second shaft portion 22d fitted into a center hole 23c of the main body base 23 and rotatably supported, and a fourth shaft portion 22g fitted into a center hole 24a of the cover 24. It has a both-end support structure in which it is rotatably supported.

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

Specifically, the energy absorbing portion E1 is formed in a fitting portion that is fitted in the output shaft 22 of the planetary carrier 62 in the axial direction. More specifically, the energy absorbing portion E1 includes a deformable portion D1 that is weakened against rotational force by forming a hollowed portion N1 in a portion of the fitting portion of the planetary carrier 62, and a deformable portion D1 that is weakened against rotational force. It includes a stopping 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 that fits into the spline hole 62a mesh with each other. It has a tooth shape in which six concave and convex teeth are arranged in rows in the rotational direction. Then, every other three of the six internal teeth meshing between the external teeth of the first spline 22c of the planetary carrier 62 are recessed from the inner circumferential side to the outer circumferential side. A hollowed-out portion N1 is formed.

Each of the hollowed out portions N1 is formed at an intermediate portion in the rotational direction of each corresponding internal tooth, that is, at an intermediate portion separated from each contact surface that contacts each external tooth of the output shaft 22 in the rotational direction. As a result, both ends of each internal tooth whose thickness has been reduced in the rotational direction by each lightened portion N1 are easily deformed plastically by being pressed in the rotational direction by each external tooth of the adjacent output shaft 22. It is configured as a weakened deformed portion D1. Each deformed portion D1 is configured to protrude inward in the radial direction by the same length as the other internal teeth (stopping portion 62c) in which the hollowed out portion N1 is not formed, and fit between the external teeth of the output shaft 22. be done.

The stopper portion 62c is formed by one of the six internal teeth of the planetary carrier 62 described above, in which the hollowed out portion N1 is not formed. With the above configuration, the stopper portion 62c has a 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, the first spline 22c of the output shaft 22 has a gap between each external tooth in the rotational direction with respect to the internal tooth (deformed portion D1) in which the hollowed out portion N1 is formed among the internal teeth of the planetary carrier 62. It is set in a packed state. However, the first spline 22c of the output shaft 22 is set in such a manner that a gap T is formed in the rotational direction with respect to each internal tooth of the planetary carrier 62 in which the hollowed out portion N1 is not formed. has been done.

With the above configuration, as shown in FIGS. 37 and 38, even if the output shaft 22 receives a large load input from the seat 1 in either direction of rotation, the output shaft 22 will first affect the deformed portion D1 of the planetary carrier 62 and its rotation. Three external teeth adjacent to each other in the direction abut each deformed portion D1 to apply a pressing force. Then, when the three external teeth of the output shaft 22 push each deformable portion D1 in the rotational direction and plastically deform it, when the rotation has progressed by the gap T, the other three external teeth It is pressed in the rotational direction against another internal tooth (stopping portion 62c) on which N1 is not formed.

As a result, the rotation of the output shaft 22 is strongly prevented by the other internal teeth (stop portion 62c) having high structural strength and in which the hollow 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 changing the posture of the seat 1.

<Summary>
To summarize the above, the seat lifter device 10 according to the first embodiment has the following configuration. Note that the reference numerals given in parentheses below 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) equipped with an output shaft (22) that moves the seat (1) up and down. This seat lifter device (10) includes a support part (S) that rotatably supports an output shaft (22), and a lock part (B) that locks rotation of the output shaft (22) with respect to the support part (S). , an energy absorption part (E1) provided in a power transmission path between the support part (S) and the output shaft (22) via the lock part (B).

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

In addition, the power transmission path includes a planetary carrier (62) that is integrally connected to the output shaft (22), and a planetary carrier (62) that is rotatably connected to the planetary carrier (62) and supported as the output shaft (22) rotates. The lock includes a plurality of planetary gears (63) that rotate and revolve around the internal gear (23e) formed in the part (S), and a sun gear (38c) that meshes with and rotates in conjunction with the plurality of planetary gears (63). The rotating member (38) whose rotation is locked by the part (B), and a planetary gear mechanism (64). The energy absorbing portion (E1) is formed in a fitting portion that is fitted in the output shaft (22) of the planetary carrier (62) in the axial direction.

According to the above configuration, even if the planetary gear mechanism (64) that speeds up the rotation of the output shaft (22) is provided, there is a gap between the output shaft (22) and the planetary carrier (62) that do not speed up the rotation of the output shaft (22). Therefore, an excessive load input to the output shaft (22) from the seat (1) side can be appropriately absorbed.

In addition, the energy absorption part (E1) has a deformation part (D1) which plastically deforms in the rotational direction when a large load of a predetermined magnitude or more in the rotational direction is input to the output shaft (22). It has a stopping part (62c) having higher structural strength than the deforming part (D1), which stops the deformation of the deforming part (D1) at a fixed position. According to the above configuration, while the deformable portion (D1) is appropriately deformed as the output shaft (22) rotates, excessive deformation of the deformable portion (D1) can be prevented by the stopping portion (62c). . Thereby, an excessive load input from the seat (1) side can be appropriately absorbed without significantly changing the posture of the seat (1).

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

Further, the output shaft (22) is connected to a power transmission portion (62) forming a power transmission path by spline fitting. The deformed portion (D1) is located in an intermediate portion of the power transmission portion (62) that is separated in the rotational direction from the contact surface between the teeth of the output shaft (22) and the teeth of the output shaft (22) that contact in the rotational direction. By forming the lightened portion (N1), a weakened structure is formed that plastically deforms in the rotational direction when a large load of a predetermined magnitude or more in the rotational direction is input. According to the above configuration, the energy absorption portion (E1) can be formed rationally and appropriately using the configuration of the spline fitting portion between the output shaft (22) and the power transmission portion (62).

Further, the energy absorbing portion (E1) is configured to plastically deform due to input of a large load in the rotational direction of a predetermined magnitude or more with respect to bidirectional rotation in the rotational direction of the output shaft (22). According to the above configuration, it is possible to appropriately absorb excessive loads in both rotational directions inputted to the output shaft (22) from the seat (1) side.

《Second embodiment》
Next, the configuration of a seat lifter device 10 according to a second embodiment of the present invention will be described using FIG. 39. In this embodiment, the rotation control device 19 is of an electric type that rotates the output shaft 73 in each direction using the rotational output of the electric motor 71 and stops the output shaft 73 from rotating using a brake force.

Specifically, the rotation control device 19 includes an electric motor 71, a housing 72, an output shaft 73, and a reduction gear 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 rotatably assembled to the housing 72.

The speed reducer 74 is configured to connect the electric motor 71 and the output shaft 73 through gears so that power can be transmitted. The reducer 74 is constituted by a gear train assembled to the housing 72 and includes a spur gear 74 a 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 part P that locks the rotation of the output shaft 73 with respect to the support part W.

The rotation control device 19 plastically deforms when a large load of a predetermined magnitude or more in the rotational direction is input to the output shaft 73 from the seat 1 side at the spline fitting portion between the spur gear 74a and the output shaft 73. The configuration includes an energy absorbing section E2. Here, the spur gear 74a corresponds to the "power transmission section" of the present invention. The energy absorbing section E2 has the same structure as the energy absorbing section 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 of a predetermined magnitude or more in the rotational direction is applied to the output shaft 73 from the seat 1 side. When input, it is configured to plastically deform and absorb energy. Therefore, description of the specific configuration of the energy absorbing section E2 will be omitted.

<Summary>
To summarize the above, the seat lifter device 10 according to the second embodiment has the following configuration. Note that the reference numerals given in parentheses below 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) that includes an output shaft (73) that moves the seat (1) up and down. This seat lifter device (10) includes a support part (W) that rotatably supports an output shaft (73), and a lock part (P) that locks rotation of the output shaft (73) with respect to the support part (W). , and an energy absorption part (E2) provided in a power transmission path between the support part (W) and the output shaft (73) via the lock part (P).

The energy absorbing portion (E2) plastically deforms when a large load of a predetermined magnitude or more in the rotational direction is input to the output shaft (73) from the seat (1) side. According to the above configuration, the energy absorbing portion (E2) can appropriately absorb an excessive load input to the output shaft (73) from the seat (1) side.

《Other embodiments》
Although the embodiments of the present invention have been described above using two embodiments, the present invention can be implemented in various forms shown below in addition to the above embodiments.

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 non-vehicle seats such as spectator seats and massage seats installed in various facilities such as sports facilities, theaters, concert venues, and event venues.

2. In addition to the structure shown in each of the above embodiments, the energy absorbing section may have another structure as shown in FIGS. 40 to 44. In the energy absorbing portion E3 shown in FIG. 40, a lightened portion N2 formed in a specific internal tooth of the planetary carrier 62 (or spur gear 74a (second embodiment)) extends over the entire area of the specific internal tooth in the rotational direction. It is formed over a period of time. With this configuration, the deformed portion D2, which is thinned in the radial direction by the hollowed out portion N2, is rotated from the external teeth of the output shaft 22 (or the output shaft 73 (second embodiment)) in the rotational direction. It has a weakened structure that is easily plastically deformed to expand outward in the radial direction due to the pressing force. Note that the configuration other than the above is the same as the configuration shown in the first embodiment, so the same reference numerals are given and the explanation will be omitted.

In the energy absorbing portion E4 shown in FIG. 41, a hollowed-out portion N3 formed in a specific internal tooth of the planetary carrier 62 (or spur gear 74a (second embodiment)) is formed on the inner circumference of the specific internal tooth and The intermediate portion of the adjacent output shafts 22 (or the output shafts 73 (second embodiment)), which leaves a contact portion with each external tooth, is hollowed out. With this configuration, the deformed portion D3 whose thickness has been reduced by the hollowed out portion N3 is pressed in the rotational direction from the external teeth of the output shaft 22 (or the output shaft 73 (second embodiment)). The hollow shape of the hollow portion N3 is easily deformed plastically in the radial direction and rotational direction by force, resulting in a weakened structure. Note that the configuration other than the above is the same as the configuration shown in the first embodiment, so the same reference numerals are given and the explanation will be omitted.

In the energy absorbing portion E5 shown in FIG. 42, a lightened portion N4 formed in a specific internal tooth of the planetary carrier 62 (or spur gear 74a (second embodiment)) is located in the middle of the specific internal tooth in the rotational direction. The part is hollowed out in a concave shape from the inner circumferential side to the outer circumferential side, and both ends of the hollowed out rotational direction are further cut into slits to the outside in the radial direction. . With such a configuration, the deformed portion D4 whose thickness has been reduced by the hollowed out portion N4 is pressed in the rotational direction from the external teeth of the output shaft 22 (or the output shaft 73 (second embodiment)). Due to the force, the structure is weakened and easily deformed plastically in the direction of rotation starting from the point deeply cut by the slit. Note that the configuration other than the above is the same as the configuration shown in the first embodiment, so the same reference numerals are given and the explanation will be omitted.

The energy absorbing portion E6 shown in FIG. 43 has hollowed out portions N5 formed in three specific internal teeth of the planetary carrier 62 (or spur gear 74a (second embodiment)), two of which are formed in specific three internal teeth. One corner of the internal tooth in the rotational direction is cut out, and the remaining corner is shaped so that the other corner of the specific inner tooth in the rotational direction is cut out. With this configuration, when the output shaft 22 (or the output shaft 73 (second embodiment)) receives a large load input from the seat side and is rotated in one direction and when it is rotated in the other direction. With this, it is possible to change the ease with which the deformable portion D5 weakened by the lightened portion N5 is deformed (rigidity of the deformable portion D5).

Therefore, for example, in response 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, the rigidity of the deformable portion D5 is made relatively high; In response to a large load that is 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 As a result, in the event of a frontal collision of the vehicle, the position of the occupant's body restraint by the seatbelt is unlikely to shift, and in the event of a rearward collision of the vehicle, energy is actively absorbed by the energy absorbing portion E6 and the seat frame It becomes possible to create a configuration that reduces the input load to the. The configuration other than the above is the same as the configuration shown in the first embodiment, so the same reference numerals are given and the explanation will be omitted.

In the energy absorbing portion E7 shown in FIG. 44, a hollow portion N6 formed in a specific internal tooth of the planetary carrier 62 (or spur gear 74a (second embodiment)) is located at the center of the specific internal tooth in the rotational direction. It is formed in a position that is biased to one side than the other parts. Even 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 rotated in one direction, and when it is rotated in the other direction, Ease of deformation (rigidity of the deformed portion D6) of the deformed portion D6 weakened by the lightened portion N6 can be changed.

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

1 Seat 2 Seat back 3 Seat cushion 3a Side frame 3a1 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 4-bar link mechanism 14 Support bracket 17 Torque rod 18 Rotation control device 19 Rotation control device 22 Output shaft 22a Pinion gear 22b First shaft portion 22c First spline 22d Second shaft portion 22e Second spline 22f Third shaft portion 22g Fourth shaft portion 23 Main body base 23a Seat portion 23b Accommodation 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 Axis 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 Center hole 38b Engaging pawl 38c Sun gear 41 Outer lever 41a Center hole 41b Through hole 41c Arm 43 Torsion spring 52 Feed pawl 52a External tooth 52b Center hole 53 Inner lever 53a Center hole 53b Stopper pin 53c Through hole 53d Axis pin 55 Torsion spring 56 Control Plate 56a Center hole 56b Hook portion 56c Connecting portion 56e Relief surface 56f Riding surface 58 Friction clutch 58a Axial pin 58b Sliding portion 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 Axis pin 62c Stop portion 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 section)
S Support part W Support part A Feed part B Lock part P Lock part N Input part G Friction generating part U Speed increase 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 (5)

A seat lifter device equipped with an output shaft for raising and lowering a seat,
a support part that rotatably supports the output shaft;
a lock portion that locks rotation of the output shaft with respect to the support portion;
An energy absorbing part provided in a power transmission path between the support part and the output shaft via the lock part, which absorbs a large load in the rotational direction of a predetermined magnitude or more from the seat side on the output shaft. the energy absorbing part that plastically deforms when input with
The power transmission path includes a planetary carrier integrally connected to the output shaft, and an internal gear rotatably connected to the planetary carrier and formed on the support portion as the output shaft rotates. A planetary gear mechanism comprising a plurality of planetary gears that revolve while rotating on their own axis, and a rotating member that includes a sun gear that meshes with the plurality of planetary gears and rotates in conjunction with the planetary gears, and whose rotation is locked by the locking part,
A seat lifter device in which the energy absorbing portion is formed in a fitting portion that is fitted in the output shaft of the planetary carrier in an axial direction . A seat lifter device equipped with an output shaft for raising and lowering a seat,
a support part that rotatably supports the output shaft;
a lock portion that locks rotation of the output shaft with respect to the support portion;
An energy absorbing part provided in a power transmission path between the support part and the output shaft via the lock part, which absorbs a large load in the rotational direction of a predetermined magnitude or more from the seat side on the output shaft. the energy absorbing part that plastically deforms when input with
The seat lifter device is configured such that the energy absorbing portion is plastically deformed by inputting a large load in the rotational direction of the predetermined magnitude or more with respect to bidirectional rotation in the rotational direction of the output shaft. The seat lifter device according to claim 1 or 2,
The energy absorption section includes a deformation section that plastically deforms in the rotational direction when a large load of the predetermined magnitude or more in the rotational direction is input to the output shaft, and a deformation of the plastically deformed deformation section at a fixed position. a stop portion having a higher structural strength than the deformation portion that stops the deformation. The seat lifter device according to claim 3,
A seat lifter device in which the output shaft is provided with a gap in the rotational direction with respect to the deformable portion. The seat lifter device according to claim 3 or 4,
The output shaft is connected to a power transmission section forming the power transmission path by spline fitting,
The deformable portion includes a hollowed out portion formed in an intermediate portion of the power transmission portion that is spaced apart in the rotational direction from a contact surface of a tooth of the output shaft that contacts the tooth of the output shaft in the rotational direction. A seat lifter device having a weakened structure that plastically deforms in the rotational direction when a large load in the rotational direction of the predetermined magnitude or more is input.

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