JP2020147267A - Lifter device - Google Patents

Abstract

To prevent sliding rotation during push-down operation and to securely lock the rotation when in the neutral position without increasing the operating load for lifting an operation handle.SOLUTION: A lifter device 10 comprises a support member S that supports an output shaft 22, an input member N that is coupled to an operation handle, a feed part A that transmits the rotation of the input member N to the output shaft 22, a lock part that rotationally locks the output shaft 22 relatively to the support member S and a friction generating part that applies a frictional force to the rotation of the output shaft 22. The friction generating part generates friction by pushing a clutch part 57a in the radial direction by the rotation of an inner lever 53 forming the input member N so that a leaf spring is pressed onto a rotating plate integrated with the output shaft 22. The inner lever 53 realizes a friction-suppressed state where it does not push the clutch part 57a in the radial direction even when the operation handle is at a neutral position or the operation handle is turned from the neutral position to upper side, whereas the inner lever realizes a friction-on state P2 where it pushes the clutch part 57a in the radial direction when the operation handle is turned from the neutral position to lower side.SELECTED DRAWING: Figure 18

Description

The present invention relates to a lifter device. More specifically, the present invention relates to a lifter device provided with an output shaft that rotates by receiving rotational power from an operation handle to raise and lower the seat.

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

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

Like the lock pole, the feed claw that rotates the feed of the gear has a pair of symmetrical claw structures so as to allow the movement of the operation handle to be returned to the neutral position when the operation is released. As the operation handle is operated, one is disengaged from the gear and the other meshes with the gear so that power can be transmitted in the feed direction, but the rotation is released in the opposite direction, which is a ratchet type meshing structure. Between the gear and the support member that supports the gear, a disc spring that can apply a sliding frictional resistance force is provided so that the gear does not slide and rotate due to the load action in the direction of gravity when the operation handle is pushed down.

Japanese Unexamined Patent Publication No. 2016-78850

In the above-mentioned conventional technique, the disc spring always applies a sliding frictional resistance force between the gear and the support member. Therefore, a sliding frictional resistance force is applied even when the operating handle is pulled up so that the gear does not slide and rotate, and the operating load becomes heavy. The present invention was devised to solve the above-mentioned problems, and the problem to be solved by the present invention is slippage during push-down operation without increasing the operation load during pull-up operation of the operation handle. The purpose is to prevent rotation and to ensure rotation lock when in the neutral position.

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

That is, the lifter device of the present invention is a lifter device provided with an output shaft that rotates by receiving rotational power from the operation handle to move the seat up and down. This lifter device transmits to the output shaft a support member that rotatably supports the output shaft, an input member that is coupled to an operation handle and is rotated around the axis of the output shaft, and a forward / reverse bidirectional rotation of the input member. It has a feed portion for locking, a lock portion for locking the rotation of the output shaft with respect to the support member, and a friction generating portion for applying a frictional force to the rotation of the output shaft. The friction generating portion is supported by the elastic body provided between the output shaft and the support member, the rotary cam connected to the input member, and the support member, and is pushed in the radial direction by the rotation of the rotary cam to be the elastic body. The clutch portion is provided between the output shaft and the rotating member that rotates integrally with the output shaft in the thrust direction to generate friction. The rotary cam is in a friction suppression state in which the operation handle is in the neutral position and even if the seat is turned in the direction of raising the seat from the neutral position, the clutch portion is not pushed in the radial direction and friction is suppressed by the elastic body. However, the operation handle is turned in the direction of lowering the seat from the neutral position to push the clutch portion in the radial direction to generate friction due to the elastic body, which is a switching structure for turning on the friction.

According to the above configuration, when the operation handle is not operated and when the seat is operated in the direction of raising the seat, the friction generating portion is in the friction suppressing state. Therefore, the operating load when the seat is raised by the operating handle does not become heavy. Further, when the operation handle is returned to the neutral position, the lock portion can be smoothly locked without being affected by friction. On the other hand, when the operation handle is operated in the direction of lowering the seat, the friction generating portion is in the friction-on state. Therefore, it is possible to appropriately prevent the output shaft from sliding and rotating due to the action of its own weight on the seat. Further, since the clutch portion presses the elastic body between the elastic body and the rotating member in the thrust direction, the rotation when the operation handle is returned to the neutral position is less likely to be hindered.

The "friction suppression state" includes a state in which friction is not generated and a state in which friction smaller than the friction-on state is generated. If the friction suppression state does not generate friction, the operating load when raising the seat by the operating handle does not become heavy. Further, when the operation handle is returned to the neutral position, the lock portion can be smoothly locked without being affected by friction. On the other hand, if the friction suppression state is a state in which a friction smaller than that in the friction on state is generated, the friction change from the friction on state can be reduced, and the operation feeling of the operation handle can be easily kept constant.

Further, the lifter device of the present invention may be further configured as follows. The lock portion has a release structure in which the operation handle is released from the lock with the support member by being rotated by a predetermined amount in each of the forward and reverse directions from the neutral position. The rotary cam pushes the clutch portion in the radial direction by rotating until the operation handle is rotated by a predetermined amount to switch to the friction-on state.

According to the above configuration, when the operation handle is operated in the direction of lowering the seat to unlock the lock portion, the friction generating portion is always in the friction-on state. Therefore, it is possible to more appropriately prevent the output shaft from sliding and rotating due to the action of its own weight on the seat.

Further, the lifter device of the present invention may be further configured as follows. The surface that supports the clutch portion with respect to the support member is an inclined surface that guides the clutch portion obliquely in the thrust direction with respect to the support member as the clutch portion moves in the radial direction by the rotary cam. ..

According to the above configuration, the clutch portion can be smoothly switched between the friction-on state and the friction suppression state in response to the movement in which the operation handle is turned in both forward and reverse directions and returned to the neutral position.

Further, the lifter device of the present invention may be further configured as follows. The member that supports the clutch portion with respect to the support member is composed of a ring-shaped guide member supported so as to be movable only in the thrust direction with respect to the support member, and the clutch portion is radially on the guide member. It is rotatably supported, and one of the rotating end of the clutch and the supporting surface on the guide member with respect to the rotating end is a spiral surface centered on the center of rotation of the clutch, and the other is the clutch. It is a contact surface that abuts and slides against the spiral surface as the clutch rotates, and the rotating end of the clutch is pushed in the radial direction by the rotating cam to rotate the clutch and guide the member. It is configured to push the elastic body in the thrust direction.

According to the above configuration, since the movement locus of the clutch portion is a rotational motion in which the center of rotation is determined, the clutch portion does not move excessively during movement, and the frictional resistance during movement is reduced. Therefore, there is an effect that the operating force for rotating the rotary cam is reduced.

Further, the lifter device of the present invention may be further configured as follows. The member that supports the clutch portion with respect to the support member comprises a guide member supported so as to be movable only in the thrust direction with respect to the support member. The clutch portion is pushed in the thrust direction between the support member and the guide member by being pushed in the radial direction by the rotary cam, and the elastic body is pushed in the thrust direction by the guide member. The guide member has a gap in the thrust direction between the guide member and the support member via the clutch portion in the friction-suppressed state.

According to the above configuration, since it is difficult for the support member and the guide member to come into direct contact with each other, it is possible to suppress the generation of abnormal noise due to the contact between the support member and the guide member.

Further, the lifter device of the present invention may be further configured as follows. The elastic body is coupled so as to be integral with the guide member in the rotational direction.

According to the above configuration, the frictional resistance exerted by the elastic body is less likely to fluctuate, so that the operation feeling of the operation handle can be kept constant.

It is an outside side view which showed the schematic structure of the lifter device which concerns on 1st Embodiment. It is a side view which looked at the structure on the outside surface side from the inside of a sheet. It is an exploded perspective view which shows the state which the operation handle and the rotation control device were removed from a seat frame. It is a perspective view which looked at the rotation control device from the outside of a seat. It is a perspective view which looked at the rotation control device from the inside of a seat. It is a front view which looked at the rotation control device from the outside of a seat. FIG. 6 is a sectional view taken along line VII-VII of FIG. FIG. 6 is a sectional view taken along line VIII-VIII of FIG. It is an exploded perspective view which looked at the rotation control device from the outside of a seat. It is an exploded perspective view seen from the inside of the sheet. FIG. 5 is an exploded perspective view showing a state in which some of the components of the rotation control device shown in FIG. 9 are assembled to each other. It is an exploded perspective view seen from the inside of the sheet. 11 is an exploded perspective view showing a state in which some of the components of the rotation control device shown in FIG. 11 are assembled to each other. It is an exploded perspective view seen from the inside of the sheet. FIG. 3 is an exploded perspective view showing a state in which some of the components of the rotation control device shown in FIG. 13 are assembled to each other. It is a state diagram of the feed part of the rotation control device when the operation handle is in a neutral position. It is a state diagram of the lock part. It is a state diagram of the feed part when the operation handle is pushed down from a neutral position. It is a state diagram of the lock part when the clutch part meshes with a friction ring by the same operation. It is a state diagram of the lock part when the lock pole is released from the lock by the same operation. It is a state diagram of the lock part when the lock part is fed and rotated by the progress of the same operation. It is a state diagram of the feed part when the operation handle is returned from the pushed down position to the neutral position. It is a state diagram of the lock part. It is a state diagram of the feed part when the operation handle is pulled up from a neutral position. It is a state diagram of the lock part when the lock pole is released from the lock by the same operation. It is a state diagram of the lock part when the lock part is fed and rotated by the progress of the same operation. It is a state diagram of the feed part when the operation handle is returned from the raised position to the neutral position. It is a state diagram of the lock part. It is a perspective view which shows the state of the input member when the operation handle is in a neutral position. It is a perspective view which shows the state of the input member when the operation handle is pushed down to the maximum position. It is a perspective view which shows the state of the input member when the operation handle is pulled up to the maximum position. It is a state diagram which the rotation of a pinion gear in a descending direction is locked by a stopper. It is a state diagram which the rotation of a pinion gear in an ascending direction is locked by a stopper. It is a state diagram which set the temporary holding member on a rotating plate. It is a state diagram which set the feed claw between a temporary holding member and a rotating plate. It is a state diagram in which a spring is set between a feed claw and a pinion gear. It is a state diagram which set the inner lever to the feed claw. It is an enlarged view of part XXXVIII of FIG. FIG. 38 is a cross-sectional view showing a state in which the friction generating portion is switched to the friction on state from FIG. 38. It is a perspective view which looked at the main part of the rotation control device of the lifter device which concerns on 2nd Embodiment from the outside of a seat. It is an enlarged perspective view of the clutch part in the guide member of a rotation control device. It is explanatory drawing which shows the assembled state of the inner lever and the clutch part of the rotation control device. FIG. 42 is an enlarged view taken along the line XXXXIII-XXXXIII in FIG. 42. It is an operation state diagram of the friction generating part when the operation handle is pushed down from a neutral position.

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

<< First Embodiment >>
1 to 3 show a seat 1 for an automobile to which the lifter device 10 according to the first embodiment of the present invention is applied. In each figure, arrows indicate the directions of each part when the seat 1 is mounted on the automobile. In the following description, the description regarding the direction shall be made with reference to this direction.

<About the schematic configuration of the lifter device 10>
As shown in FIG. 1, the seat 1 is provided with a seat back 3 forming a backrest at the rear portion of the seat cushion 2 forming a seat portion, and the seat back 3 adjusts the backrest angle in the front-rear direction with respect to the seat cushion 2. It is connected so that it can be done. The seat cushion 2 is provided with a lifter device 10 and a seat slide device 8 at the lower portion, and is fixed to the floor 4 of the vehicle via a bracket 7.

As shown in FIG. 2, the seat slide device 8 is known, and a pair of left and right upper rails 6 are coupled to a pair of left and right lower rails 5 extending in the front-rear direction so as to be slidable back and forth. The left and right lower rails 5 are fixedly supported by a pair of front and rear brackets 7 fixed to the floor 4. Lifter devices 10 are provided on the left and right upper rails 6.

As shown in FIGS. 2 and 3, the lifter device 10 includes a support bracket 14 fixed on each upper rail 6 and a plurality of link members 11 rotatably connected to the front and rear portions of each upper rail 6, and is a seat. The side frame 13, the support bracket 14, which is a skeleton member of the cushion 2, and each link member 11 constitute a link mechanism 12 which is a four-section link. Of the plurality of link members 11, the rear link 11b on the right rear side is configured to include a sector gear 16 and is configured to be rotated in the front-rear direction by the pinion gear 18 of the rotation control device 21. The rotation axis of the rear link 11b on the right rear side with respect to the side frame 13 is composed of a torque rod 17, and the rear link (not shown) on the left rear side is also synchronized with the rear link 11b via the torque rod 17. It is configured to rotate.

A through hole 13a for inserting the pinion gear 18 is bored in the side frame 13, and the rotation control device 21 is fixed to the right wall of the side frame 13 so that the pinion gear 18 is inserted into the through hole 13a. ing. The rotation control device 21 can be rotated in both forward and reverse directions by an operation handle 20 provided on the right side of the seat cushion 2 extending in the front-rear direction. When the operation handle 20 is rotated upward from the neutral position, the rotation control device 21 rotates in the direction of raising the rear link 11b from the support bracket 14. When the operation handle 20 is rotated downward from the neutral position, the rotation control device 21 rotates in a direction in which the rear link 11b is turned down on the support bracket 14. With the above-described four-section link configuration, the front link 11a also rotates according to the rotation of the rear link 11b, and the height position of the seat cushion 2 with respect to the floor 4 is adjusted according to the operation of the operation handle 20.

<About the configuration of the rotation control device 21>
4 to 6 show a state in which the rotation control device 21 is removed from the seat cushion 2. Hereinafter, the configuration of the rotation control device 21 will be described with reference to FIGS. 4 to 15. For the reference numerals of the respective constituent members of the rotation control device 21 described below, any one of FIGS. 4 to 15 above shall be referred to as appropriate.

The rotation control device 21 is assembled so that the output shaft 22 is passed through the center hole 23c of the base 23, which is a support member, from the right side, and the pinion gear 18 projects from the left side surface of the base 23. Then, the base 23 is fixed to the side frame 13 in a state where the pinion gear 18 penetrates the through hole 13a of the side frame 13.

The right side surface of the base 23 is punched to the left side so as to accommodate the disk-shaped rotating plate 31 to form a guide recess 23b, and has a circular container shape as a whole. Internal teeth 34 in which four poles 32 and 33, which will be described later, mesh with each other are formed on the inner peripheral surface of the guide recess 23b. A spline hole 31b is formed in the center of the rotating plate 31 so as to fit with the spline 22b formed on the output shaft 22. Therefore, the rotating plate 31 is integrally rotated with the output shaft 22. Here, the rotating plate 31 corresponds to the "rotating member" of the present invention.

On the outer peripheral portion of the right side surface of the rotating plate 31, one protrusion 31d is formed in a pin shape by being dispersed vertically, and a total of four protrusions 31e are formed in a pin shape by being dispersed in the front and rear to form a pair of upper and lower protrusions. Has been done. Through holes 32a and 33a of the poles 32 and 33 are rotatably fitted to the protrusions 31e, and the poles 32 and 33 are swingable around the protrusions 31e. Further, a winding portion 35a of the torsion spring 35 is fitted to each protrusion 31d. Each end 35b of the torsion spring 35 is engaged with the poles 32 and 33, and urges the poles 32 and 33 toward the outer peripheral side of the rotating plate 31. Therefore, the engaging ends 32c and 33c forming the outer teeth of the poles 32 and 33 are always meshed with the inner teeth 34 of the base 23.

On the right side surface of the cover 24 formed in the shape of a container bulging to the right as a whole, a plate shape forming an outer member of the input member N having an inner / outer double structure that is coupled to the operation handle 20 and is rotated. An outer lever 41 is provided. A round bar-shaped end 22c forming the right end of the output shaft 22 is inserted through the central through hole 24e of the cover 24 and the center hole 41b of the outer lever 41 from the left side. By the above insertion, the outer lever 41 is supported with respect to the cover 24 so as to be rotatable about the end portion 22c of the output shaft 22. Further, each of the pair of arcuate through holes 24a formed in the cover 24 and the pair of round hole-shaped through holes 41a formed in the outer lever 41 have a plate shape forming an inner member of the input member N. A pair of stopper pins 53a protruding to the right (thrust direction) from the inner lever 53 of the above are inserted from the left side.

Each of the pair of stopper pins 53a is inserted into the inner lever 53 from the right direction and is integrally crimped. The pair of stopper pins 53a are passed through the corresponding through holes 24a of the cover 24 from the left side. Then, the pair of stopper pins 53a are inserted into the corresponding through holes 41a of the outer lever 41 set in a superposed manner on the right side surface of the cover 24, and are integrally coupled with the outer lever 41.

By the above coupling, the inner lever 53 and the outer lever 41 are assembled so as to be integrally able to rotate relative to the cover 24 around the output shaft 22. At the lower part of the outer lever 41, an engaging piece 42 that is bent to the left and extends is formed. The engaging pieces 42 are set side by side on the outer peripheral side of the engaging pieces 24b cut up from the lower part of the cover 24 to the right side.

An end portion 43a of a ring-shaped torsion spring 43 is hung between the engaging pieces 42 and 24b. Therefore, when the outer lever 41 is rotationally operated by the operation handle 20, the engaging piece 42 moves so as to be separated from the engaging piece 24b in the rotational direction, but when the rotational operation is released, the torsion spring 43 is attached. By the force, the engaging piece 42 and the engaging piece 24b are returned to the overlapping state in the rotation direction, and the outer lever 41 is returned to the neutral position before the rotation operation.

Further, on the left side of the cover 24, an inner lever 53 and a temporary holding member 54 are provided so as to be housed in the container shape of the cover 24. The cover 24 is fixed to the base 23 by sandwiching these parts together with the rotation plate 31 and the rotation transmission plate 36. At this time, the legs 24d of the cover 24 are fixed to the through holes 23a of the base 23 by rivets (not shown).

On the upper part of the cover 24, riding portions 24c protruding to the left side are formed at two positions in front of and behind the cover 24. These riding portions 24c are formed by cutting up a part of the cover 24 to the left side with the inner peripheral side as a base point. Each of these riding portions 24c is formed in a curved plate shape curved in a shape forming an arc of the same circle drawn around the center of the cover 24. As will be described later in FIGS. 18 and 24, when the inner lever 53 is turned clockwise (see FIG. 18) or counterclockwise (see FIG. 24) by operating the operation handle 20, the riding portion 24c is provided. Of the pair of feed claws 52 attached to the inner lever 53, one of the feed claws 52 that does not have a feed function is made to ride on and is released from the meshed state with the internal teeth 51 of the rotation transmission plate 36.

As shown in FIGS. 34 to 37, the temporary holding member 54 is set on the right side surface of the rotation transmission plate 36 described later, and a pair of feed claws 52 and these feed claws 52 are provided to the rotation transmission plate 36. It is a temporary holder that holds the torsion spring 55 that urges the rotation transmission plate 36 in the direction of meshing with the internal teeth 51 in a positioned state. The internal teeth 51 of the rotation transmission plate 36 and the internal teeth 34 of the base 23 have the same number of teeth.

As shown in FIG. 34, the temporary holding member 54 has a cylindrical shaft support portion 54b formed at the center thereof, which is passed through the center hole 36d of the rotation transmission plate 36 from the left side at the right end of the output shaft 22. It is passed through the portion 22c and set on the right side surface of the rotation transmission plate 36. With this set, the temporary holding member 54 is supported with respect to the rotation transmission plate 36 so as to be rotatable about the end portion 22c of the output shaft 22.

The temporary holding member 54 further has a feed claw holding portion 54a that projects outward in the radial direction from a partial region in the rotational direction of the shaft support portion 54b. The temporary holding member 54 holds a pair of feed claws 52 in a state of being applied on each side surface in the rotation direction of the feed claw holding portion 54a projecting outward in the radial direction. Specifically, the feed claw holding portion 54a has a pair of rotation receiving surfaces 54a1 recessed in a concave curved surface shape on each side surface in the rotation direction thereof.

The feed claw holding portion 54a is provided with an outer peripheral surface of each feed claw 52 on the hinge portion 52b side on each rotation receiving surface 54a1 recessed in a concave curved surface shape, and each feed claw 52 is placed on each rotation receiving surface. It is guided so as to be slid and rotated in and out in the radial direction along the concave curved surface of 54a1 (see FIG. 35). Specifically, each feed claw 52 is set in a state in which an arc-shaped outer peripheral surface curved around the hinge portion 52b is applied to each rotation receiving surface 54a1, and is set on each rotation receiving surface 54a1. Along the guide, the hinge portion 52b, which is the center of rotation of each of them (each feed claw 52), is guided so that it can slide and rotate in and out in the radial direction.

Therefore, after setting the pair of feed claws 52 so as to be applied to each of the rotary receiving surfaces 54a1 of the temporary holding member 54, the pair of feed claws 52 are slid outward in the radial direction along the respective rotary receiving surfaces 54a1. By rotating the feed claws 52, the pair of feed claws 52 can be set in a state in which the engaging end portions 52a forming the outer teeth of the feed claws 52 are meshed with the inner teeth 51 of the rotation transmission plate 36. Then, after the setting, as shown in FIG. 36, the torsion spring 55 is hung between the end portion 22c of the output shaft 22 through which the shaft support portion 54b of the temporary holding member 54 is passed and the pair of feed claws 52. As a result, the pair of feed claws 52 can be pressed against the internal teeth 51 of the rotation transmission plate 36 by the spring urging force of the torsion spring 55 and held in a meshed state.

In the torsion spring 55, the winding portion 55a wound in a circular shape at the center thereof is passed through the end portion 22c of the output shaft 22, and each end portion 55b extending from the winding portion 55a is a pair of feed claws 52. It is set so that it is pressed against the inner peripheral surface. As a result, the torsion spring 55 is set in a state in which a urging force is applied to engage the pair of feed claws 52 with the internal teeth 51 of the rotation transmission plate 36 with the output shaft 22 as a fulcrum.

With the above set, as shown in FIG. 37, the pair of feed claws 52 are in a state of being aligned with the position where the inner lever 53 can be inserted and set from the right side thereof. Specifically, the inner lever 53 is assembled to the pair of feed claws 52 set so as to pass the end portion 22c of the output shaft 22 into the center hole 53d from the right side of the rotation transmission plate 36. Each hinge portion 52b protruding from the right side surface of each feed claw 52 in a pin shape can be inserted into and assembled into the two through holes 53b formed in the 53 in a round hole shape. The pair of feed claws 52 are connected to the inner lever 53 so that they can rotate about the hinge portions 52b by inserting the corresponding through holes 53b of the inner lever 53 into the hinge portions 52b. Will be done.

Therefore, by setting (temporarily holding) the pair of feed claws 52 and the torsion spring 55 on the rotation transmission plate 36 using the temporary holding member 54, each feed claw 52 urged by the torsion spring 55 is manually held. The inner lever 53 can be easily connected to the pair of feed claws 52 placed on the rotation transmission plate 36 without requiring holding work such as pressing. The temporary holding member 54 is made of resin, and by connecting the inner lever 53 to the pair of feed claws 52, the temporary holding member 54 can rotate integrally with the inner lever 53 via the pair of feed claws 52. It is designed to be connected to. Each component of the rotation control device 21 other than the temporary holding member 54 is made of a metal member.

As shown in FIG. 9, the temporary holding member 54 further extends in a fan shape outward in the radial direction from a part of the rotation direction facing the forming region of the feed claw holding portion 54a of the shaft support portion 54b. It has a part 54c. The spacer portion 54c is interposed between the set rotation transmission plate 36 and the facing portion 53e of the inner lever 53 in the thrust direction, and functions to secure a space in the thrust direction between them. By interposing the spacer portion 54c, the inner lever 53 can be smoothly rotated with respect to the rotation transmission plate 36.

As shown in FIG. 9, the inner lever 53 has a configuration in which round pin-shaped stopper pins 53a are coupled to two front and rear portions on a substantially disk-shaped facing portion 53e whose surface faces in the thrust direction. To. Each stopper pin 53a projects to the right from above the facing portion 53e of the inner lever 53, passes through each of the corresponding through holes 24a of the cover 24, and is inserted into each of the corresponding through holes 41a of the outer lever 41. It is integrally connected with 41.

Each of the through holes 24a of the cover 24 has a hole shape extending in a long shape in the rotation direction. As shown in FIG. 29, these through holes 24a position each stopper pin 53a at the center position in the rotational direction when the inner lever 53, which is the input member N, is in the neutral position before operation. As shown in FIG. 30, each through hole 24a abuts each stopper pin 53a on the corresponding end surface in the rotation direction when the inner lever 53 is pushed down from the neutral position, and the inner lever 53 (input member N) ) Locks the rotational movement in the downward direction. Further, as shown in FIG. 31, each through hole 24a abuts each stopper pin 53a on the corresponding end surface in the rotation direction even when the inner lever 53 is pulled up from the neutral position, and the inner lever 53 Locks the rotational movement of (input member N) in the pulling direction.

A pair of feed claws 52 are assembled on the left side surface of the inner lever 53 in a rotatable state. A rotation transmission plate 36 having a substantially disk shape is provided on the left side of the inner lever 53. The rotation transmission plate 36 is arranged so as to be sandwiched between the inner lever 53 and the rotation plate 31. On the left side surface of the rotation transmission plate 36, a substantially disk-shaped control plate 56 is assembled so as to be integrated in the rotation direction.

The control plate 56 is assembled to the left side surface portion of the rotation transmission plate 36 so as to be integrated in the rotation direction. Specifically, the control plate 56 is a spline fitting portion that is semi-punched so as to project into a spline hole 56a formed through the center thereof in a substantially cylindrical shape from the center of the rotation transmission plate 36 to the left side. By fitting the 36a, the rotation transmission plate 36 and the rotation transmission plate 36 are assembled in an integral state in the rotation direction.

On the outer peripheral portion of the control plate 56, a control hole 56b that receives pins 32b and 33b protruding to the right from the poles 32 and 33 from the left side and controls the lock / unlock operation of the poles 32 and 33 is provided. It is formed at four positions in the rotation direction. Further, on the disk surface portion of the control plate 56, each protrusion 31d protruding in a pin shape from the corresponding two positions of the rotating plate 31 to the right side is formed from the left side at two positions facing each other in the rotation direction. An engaging elongated hole 56c for receiving is formed.

These engaging elongated holes 56c have an elongated hole shape extending in the rotational direction. As shown in FIG. 17, each engaging slot 56c is in a neutral position due to the urging of a torsion spring 37 in which the rotation position of the control plate 56 (rotation transmission plate 36) with respect to the rotation plate 31 is engaged between the two. When held, each protrusion 31d of the rotating plate 31 is positioned at a substantially central position of the elongated hole shape. As a result, each engaging slot 56c allows the control plate 56 (rotation transmission plate 36) to rotate in the forward and reverse directions with respect to the rotation plate 31 from the above state.

However, in each engaging slot 56c, as shown in FIGS. 21 and 26, the control plate 56 (rotation transmission plate 36) is rotated clockwise with respect to the rotation plate 31 by the operation of the operation handle 20 (see FIG. 21). Alternatively, by rotating counterclockwise in the drawing (see FIG. 26), each protrusion 31d is brought into contact with the corresponding end surface in the direction of rotation. As a result, the rotation plate 31 is integrated with the control plate 56 (rotation transmission plate 36) from that point onward and is rotated in the rotation direction thereof.

The ring-shaped torsion spring 37 that is hooked between the rotation transmission plate 36 and the rotation plate 31 is rotated with the elongated hole 36c of the rotation transmission plate 36 by bending the ends 37a on both sides thereof to the left side. It is inserted across the elongated hole 31c of the plate 31. As a result, the torsion spring 37 is in a state of exerting an urging force in both directions in the rotation direction across the elongated holes 36c and 31c. The torsion spring 37 maintains the rotation angle of the rotation transmission plate 36 with respect to the rotation plate 31 in a neutral position by its urging force.

Here, FIGS. 9 to 10 show a state in which the components of the rotation control device 21 are disassembled into pieces. Further, in FIGS. 11 to 12, the poles 32 and 33 and the torsion springs 35 are assembled to the rotating plate 31, the feed claws 52 and the torsion springs 55 are assembled to the inner lever 53, and the torsion is further attached to the cover 24. The state in which the spring 43 is assembled is shown. Further, FIGS. 13 to 14 show a state in which the rotary plate 31 is assembled to the base 23 and the control plate 56 is assembled to the rotary transmission plate 36.

Further, FIG. 15 shows a state in which the rotation transmission plate 36 is assembled to the rotation plate 31 (see FIG. 13) assembled to the base 23, and the feed claws 52 and the inner lever 53 are attached to the rotation transmission plate 36. It is shown. Each of the above figures does not show the assembling procedure of the rotation control device 21, but shows the assembling state of each component. The rotation control device 21 is actually set and assembled in the direction of gravity in order from the left side shown in each component shown in FIG. 9.

Here, as shown in FIG. 9, a pair of feed claws 52 and the feed claw 52 which are connected to the above-mentioned inner lever 53 (input member N) and transmit the rotation-operated movement to the rotation transmission plate 36 as feed rotation. The rotation transmission plate 36 that rotates by receiving the transmission of rotational power from, the control plate 56 that is integrally connected to the rotation transmission plate 36, and the control plate 56 (rotation transmission plate 36) are integrally connected from the middle. The mechanism including the rotating plate 31 that rotates as a feed unit A is a feed portion A that transmits the rotation of the inner lever 53 (input member N) to the output shaft 22 as a feed rotation. Further, the lock structure by urging the poles 32 and 33 that lock the rotation of the pinion gear 18 fed and rotated by the feed portion A with respect to the base 23 is referred to as the lock portion B. Further, the structure including the base 23 and the cover 24 integrally assembled to the base 23 is referred to as the support member S.

A concentrically curved outer peripheral surface 22a having no gear shape is formed between the pinion gear 18 of the output shaft 22 and the spline 22b. A rotation shaft side protrusion 63 that partially protrudes outward in the radial direction is formed in a part of the outer peripheral surface 22a in the rotation direction. The rotating shaft side protrusion 63 is set on the right side surface of the guide recess 23b of the base 23 by inserting the pinion gear 18 into the center hole 23c of the base 23 from the right side.

An arcuate support member side protrusion 61 is formed on the right side surface of the guide recess 23b of the base 23. On the other hand, as shown in FIG. 10, a sliding surface portion forming a cylindrical inner peripheral surface is formed around the spline hole 31b of the rotating plate 31 due to the central portion of the rotating plate 31 being semi-cut into a cylindrical shape on the right side. 31a is formed. The sliding surface portion 31a is set so as to form concentric circles with the spline hole 31b, and when the rotating plate 31 rotates with respect to the base 23, the outer circumference of the support member side protrusion 61 is on the inner circumference of the sliding surface portion 31a. Is designed to slide. Further, the engaging piece 62 is arranged so as to slide in the gap between the inner circumference of the sliding surface portion 31a and the outer peripheral surface 22a of the output shaft 22.

Therefore, when the output shaft 22 is rotated in the downward direction by the operation of the rotation control device 21 and reaches the lower limit position, the rotating shaft side protrusion 63 sandwiches the engaging piece 62 and the support member side as shown in FIG. It comes into contact with the end surface of the protrusion 61, and further rotation of the output shaft 22 is stopped. Further, the output shaft 22 is rotated in the ascending direction by the operation of the rotation control device 21, and when the upper limit position is reached as shown in FIG. 33, the rotating shaft side protrusion 63 sandwiches the engaging piece 62 between the support member side. It comes into contact with the end surface on the opposite side of the protrusion 61, and further rotation of the output shaft 22 is stopped. The stopper 60 is configured as a mechanism in which the rotating shaft side protrusion 63 is abutted against the support member side protrusion 61 in the rotation direction with the engaging piece 62 sandwiched between them to stop the rotation of the output shaft 22.

As shown in FIG. 9, a friction generating portion 57 that imparts a sliding friction resistance force to the rotational movement of the rotating plate 31 with respect to the supporting member S between the base 23 and the cover 24 forming the supporting member S and the rotating plate 31. Is provided. The friction generating portion 57 includes a ring-shaped guide member 57c provided on the left side surface portion of the cover 24 and three clutches provided in a state of being guided at three positions in the rotation direction of the guide member 57c. A leaf spring 57b provided on the left side of the guide member 57c and having a ring shape bent into a corrugated shape having substantially the same diameter, and a rotation forming a ring shape having substantially the same diameter provided on the left side of the leaf spring 57b. It is composed of a ring 57d and a fixed ring 57e. Here, the leaf spring 57b corresponds to the "elastic body" of the present invention.

The guide member 57c is assembled so as to be slidable only in the thrust direction with respect to the left side surface portion of the cover 24. Specifically, in the guide member 57c, round pin-shaped engaging projections 57c1 protruding from the right side surfaces of the two left and right positions are formed at two corresponding positions of the cover 24, and the round hole-shaped engaging projections 57c1 are formed. It is inserted and set in the hole 24f from the left side. As a result, the guide member 57c is assembled with respect to the cover 24 so as to be integral with the cover 24 in the rotational direction and the radial direction, but slidable in the thrust direction.

The three clutch portions 57a are set in the corresponding inclined concave surfaces 57c2 formed at three positions in the rotation direction of the right side surface portion of the guide member 57c. With the same set, as shown in FIG. 38, each clutch portion 57a is arranged so as to be sandwiched in the thrust direction between each inclined concave surface 57c2 formed on the right side surface portion of the guide member 57c and the left side surface of the cover 24. .. As a result, each clutch portion 57a can be slidable only in the diagonal radial direction in the thrust direction along the inclination direction of each inclined concave surface 57c2 by the inclined concave surface 57c2 of the guide member 57c from both sides in the rotation direction. It is supported. Inside each clutch portion 57a in the radial direction, the above-mentioned substantially disk-shaped inner lever 53 is arranged. Here, the inner lever 53 corresponds to the "rotary cam" of the present invention. Further, each inclined concave surface 57c2 corresponds to the "inclined surface" of the present invention.

As shown in FIG. 9, the inner lever 53 has a relief surface 53f partially recessed inward in the radial direction and a ride bulging outward in the radial direction at three positions on the outer peripheral surface in the circumferential direction. The rising surface 53 g is formed so as to be arranged side by side in the rotation direction. Each of the relief surfaces 53f and the riding surface 53g has a shape curved in an arc shape concentric with each other drawn around the center of the inner lever 53, respectively. The stepped surface between each relief surface 53f and each climbing surface 53g is an inclined surface 53h that connects the two in an inclined shape instead of a right angle.

As shown in FIGS. 16 and 38, each of the clutch portions 57a is at a boundary with an inclined surface 53h on the corresponding relief surface 53f on the outer peripheral surface of the inner lever 53 when the inner lever 53 is in the neutral position before operation. It is designed to be located. As shown in FIG. 24, each of the clutch portions 57a slides on the corresponding relief surface 53f of the inner lever 53 even when the inner lever 53 is rotated in the direction of ascending rotation of the output shaft 22 from the neutral position. The position of the guide member 57c in the corresponding inclined concave surface 57c2 is not changed (friction suppression state P1: see FIG. 38).

However, as shown in FIG. 18, each clutch portion 57a rides up from the corresponding inclined surface 53h of the inner lever 53 at the same time when the inner lever 53 is rotated in the downward rotation direction of the output shaft 22 from the neutral position. It slides onto the surface 53g and is pushed outward in the radial direction along the corresponding inclined concave surface 57c2 of the guide member 57c (friction on state P2: see FIG. 39).

As a result, each clutch portion 57a pushes the guide member 57c to the left side (thrust direction) with the contact point pressed against the left side surface of the inner lever 53 as a fulcrum, and presses the guide member 57c against the leaf spring 57b. Then, the leaf spring 57b pushed to the left side is pressed against the rotating ring 57d provided on the left side of the leaf spring 57b. Further, the pressed rotating ring 57d is pressed against the fixing ring 57e provided on the left side thereof. The rotating ring 57d is connected to the rotating plate 31 in a rotational direction, and the fixing ring 57e is connected to the base 23 (support member S) in a rotational direction. ing. Therefore, by each of the above pressings, a sliding friction resistance force is applied to the rotational movement of the rotating plate 31 with respect to the base 23.

As shown in FIG. 9, three rotating rings 57d are provided side by side in the thrust direction, and two fixing rings 57e are provided side by side in the thrust direction so as to be sandwiched between the rotating rings 57d one by one. Has been done. Each of the rotating rings 57d is assembled so as to be slidable only in the thrust direction with respect to the right side surface portion of the rotating plate 31. Specifically, in the rotating ring 57d, each of the round hole-shaped first engaging holes 57d1 formed in each piece protruding inward in the radial direction from the inner peripheral edges of the two upper and lower portions on the left side rotates. It is inserted and set from the right side into each first engaging pin 31f having a round pin shape protruding to the right side from two corresponding positions of the plate 31. As a result, the two rotating rings 57d on the left side are integrated with the rotating plate 31 in the rotational direction and the radial direction, but are assembled so as to be slidable in the thrust direction.

Further, in the remaining one rotating ring 57d on the right side, each of the round hole-shaped second engaging holes 57d2 formed in each piece protruding inward in the radial direction from the inner peripheral edges of the two upper and lower portions is the rotating plate 31. It is inserted and set from the right side into each of the second engaging pins 31g having a round pin shape protruding to the right side from the corresponding two positions. As a result, the one rotating ring 57d on the right side is also integrated with the rotating plate 31 in the rotational direction and the radial direction, but is assembled so as to be slidable in the thrust direction.

The first engaging pin 31f and the second engaging pin 31g formed on the rotating plate 31 are formed at positions deviated from each other in the rotational direction. Then, each of the second engaging holes 57d2 formed in the one rotating ring 57d on the right side inserted into each of the second engaging pins 31g is bent to the left from the inner peripheral edge portion of the rotating ring 57d in the radial direction. It is formed on each piece of the crank shape that overhangs inward. With such a configuration, the protruding lengths of the first engaging pin 31f protruding to the right from the rotating plate 31 and the second engaging pin 31g are divided into two parts and kept short. ..

On the other hand, each of the two fixing rings 57e is assembled so as to be slidable only in the thrust direction with respect to the outer peripheral edge portion of the base 23. Specifically, in the fixing ring 57e, each engaging claw 57e1 that is bent to the left from the four outer peripheral edges in the rotation direction is formed on the corresponding four outer peripheral edges of the base 23. It is inserted and set in each engaging groove 23d from the right side. As a result, the fixing ring 57e is assembled with respect to the base 23 so as to be integral with the base 23 in the rotational direction and the radial direction, but slidable in the thrust direction.

When the rotating ring 57d and the fixing ring 57e having the above configuration receive a pressing force from the right side by the leaf spring 57b, the rotating ring 57d slides to the left side with respect to the rotating plate 31, and the fixing ring 57e is attached to the base 23. On the other hand, while sliding to the left side, they are pressed against each other in a thrust direction. Then, the leftmost rotating ring 57d is pressed against the right side surface on the outer peripheral side of the internal teeth 34 of the base 23. Therefore, when the rotary plate 31 is rotated in the direction of lowering and rotating the output shaft 22 from the above state, the leaf spring 57b is fixed to each rotary ring 57d by the force pressed against the right rotary ring 57d and the force. A sliding friction resistance force is applied to the rotational movement of the rotating plate 31 with respect to the base 23 by the force of pressing the ring 57e against each other in the thrust direction and the force of pressing the left rotating ring 57d onto the right surface of the base 23. To.

The above-mentioned sliding friction resistance force can be obtained as a force for rubbing a plurality of rotating rings 57d and fixing rings 57e in a laminated manner by the elastic force exerted by one leaf spring 57b. Therefore, by setting one leaf spring 57b, a large sliding friction resistance force corresponding to the set number of rotating rings 57d can be obtained. As shown in FIG. 16, each clutch portion 57a is in a friction suppressing state P1 in which the inner lever 53 is not pushed outward in the radial direction when the inner lever 53 is in the neutral position before operation. In that state, as shown in FIG. 38, the guide member 57c that guides each clutch portion 57a is not pushed in the thrust direction by each clutch portion 57a, but is connected to the left side surface of the cover 24 via each clutch portion 57a. It is assumed that there is a gap T (see FIG. 7) in the thrust direction between the two.

That is, even when the guide member 57c is not affected by the friction suppressing state P1, that is, the elastic force in the thrust direction by the leaf spring 57b, the guide member 57c has a gap T in the thrust direction between the guide member 57c and the left side surface of the cover 24. It is set to have. As a result, the guide member 57c is less likely to generate an abnormal noise due to rubbing or hitting the left side surface of the cover 24 in the friction suppression state P1. Further, as shown in FIG. 39, the guide member 57c covers the guide member 57a with the guide member 57a even when the clutch portions 57a are pushed outward in the radial direction and switched to the friction-on state P2. By being pushed in the thrust direction between the left side surface of the cover 24 and the left side surface of the cover 24, a gap T in the thrust direction is provided between the left side surface and the cover 24. As a result, the guide member 57c is less likely to generate abnormal noise due to rubbing or hitting the left side surface of the cover 24 even in the friction-on state P2.

As shown in FIG. 10, the guide member 57c has a flange portion 57c3 that projects substantially cylindrically to the left from the inner peripheral edge of the ring shape. The flange portion 57c3 is set in the ring of the leaf spring 57b, supports the leaf spring 57b from the inner peripheral side, and holds the leaf spring 57b at a position concentric with the guide member 57c. The leaf spring 57b is connected to the guide member 57c in a state of being integrated in the rotational direction. Specifically, the locking claw 57b1 protruding inward in the radial direction from the inner peripheral edge portion of the leaf spring 57b has a diameter in the locking hole 57c4 formed at the corresponding portion of the flange portion 57c3 of the guide member 57c. By fitting from the outside in the direction, the leaf spring 57b is connected to the guide member 57c in a state of being integrated in the rotation direction. As a result, the leaf spring 57b does not rotate, and the frictional resistance exerted by the leaf spring 57b is less likely to fluctuate, so that the operation feeling of the operation handle 20 can be kept constant.

<Action of rotation control device 21 (operation handle 20 is not operated)>
Hereinafter, the height adjusting action of the seat cushion 2 by the rotation control device 21 will be described with reference to FIGS. 16 to 28.

16 and 17 show a neutral position in which the operation handle 20 is not operated and the outer lever 41 and the inner lever 53 forming the input member N are not rotated. At this time, as shown in FIG. 16, the feed claw 52 is in a state in which the engaging end portion 52a forming the outer teeth of the feed claw 52 is engaged with the inner teeth 51 of the rotation transmission plate 36 by the urging of the torsion spring 55. Further, as shown in FIG. 17, the poles 32 and 33 are in a state in which the engaging end portions 32c and 33c forming their outer teeth are engaged with the inner teeth 34 of the base 23 by the urging of the torsion springs 35. Has been done. Therefore, the rotation of the rotating plate 31 is locked through the engagement of the poles 32 and 33, and the height of the seat 1 is not changed to the ascending side or the descending side. Further, each clutch portion 57a is located on the corresponding relief surface 53f of the inner lever 53, and the friction suppression state P1 for suppressing the generation of friction is set.

<Action of rotation control device 21 (operation to push down the operation handle 20)>
18 to 21 show a state in which the operation handle 20 is pushed down from the neutral position. At this time, as shown in FIG. 18, the inner lever 53 is rotated in the direction of the arrow by the rotation of the outer lever 41. As a result, each feed claw 52 is moved in the same direction. Therefore, the engaging end portion 52a forming the outer tooth of the feed claw 52 on the front side transmits a force to the inner tooth 51 of the rotation transmission plate 36, and pushes the rotation transmission plate 36 in the direction of the arrow. At this time, the engaging end portion 52a forming the outer teeth of the rear feed claw 52 is in a state of not meshing with the inner teeth 51 of the rotation transmission plate 36. That is, as the rotation transmission plate 36 rotates, the rear feed claw 52 rides on the riding portion 24c on the same side, and the engaging end portion 52a is separated from the meshing with the internal teeth 51. ..

When the inner lever 53 is turned as described above, each clutch portion 57a rides on the corresponding riding surface 53g of the inner lever 53 and is switched to the friction-on state P2. At that time, as shown in FIG. 19, the poles 32 and 33 are still held in a state of being meshed with the internal teeth 34 of the base 23. Then, when the rotation transmission plate 36 is further rotated by the inner lever 53 from the above state, as shown in FIG. 20, two control holes 56b of the control plate 56 integrally with the rotation transmission plate 36 are diagonally positioned. Engage with the pin 33b of the pole 33 and push the engaging end 33c of each pole 33 inward in the radial direction so as to disengage from the meshing with the internal teeth 34 of the base 23.

Specifically, as shown in FIG. 17, the four control holes 56b formed in the control plate 56 are in a neutral position when the rotation transmission plate 36 is urged by the torsion spring 37 with respect to the rotation plate 31. Occasionally, the pins 32b and 33b of the poles 32 and 33 are positioned as follows. That is, the corresponding two control holes 56b into which the pins 32b of the two poles 32 at the diagonal positions are inserted have the inclined side surfaces in which the surfaces are directed in the rotation direction of the pins 32b in the counterclockwise direction shown in the drawing. It is positioned at a position that is close to it and is biased in the direction of rotation. Further, the corresponding two control holes 56b into which the pins 33b of the two poles 33 at other diagonal positions different from the above are inserted have inclined side surfaces that face each pin 33b in the direction of rotation. It is positioned at a position that is biased in the direction of rotation, close to the clockwise direction shown in the figure.

With such a configuration, the rotation transmission plate 36 is rotated in the clockwise direction shown in FIG. 20 from the above-mentioned neutral position, so that the two poles 33 at the above-mentioned diagonal positions are formed. The inclined side surfaces of the two control holes 56b into which the pins 33b are inserted are brought into contact with the two pins 33b, and each pin 33b has a diameter along the inclined side surface of each control hole 56b as its rotation progresses. While pushing and sliding inward in the direction, leaving the engaging end 32c of the other two poles 32 in mesh with the internal teeth 34 of the base 23, the engaging end 33c of each pole 33 is attached to the base 23. It is designed to be removed from the mesh with the internal teeth 34.

As a result, the locked state of the rotating plate 31 in the downward rotation direction is released. After that, when each protrusion 31d of the rotating plate 31 comes into contact with the end of each engaging elongated hole 56c of the control plate 56, the rotation of the rotation transmitting plate 36 is transmitted to the rotating plate 31. Therefore, as shown in FIG. 21, the rotary plate 31 is fed and rotated in the clockwise direction shown in which the rotation transmission plate 36 is fed and rotated with respect to the base 23, and the output shaft 22 integrally with the rotating plate 31 is in the same direction. Can be fed and rotated integrally with. At this time, the engaging end portions 32c of the two poles 32 at other diagonal positions are prevented from engaging with the internal teeth 34 of the base 23. That is, in this state, the tooth of the engaging end portion 32c receives the load in the normal direction of the tooth of the internal tooth 34 and is moved in the meshing release direction. Therefore, when the rotating plate 31 rotates, the engaging end portions 32c of the two poles 32 are slid so as to slide on the internal teeth 34 of the base 23.

When the feed rotation of the rotation plate 31 by the rotation transmission plate 36 is stopped and the operation handle 20 is returned to the neutral position as shown in FIG. 22, the two poles 33 at the diagonal positions of the release operation are stopped. As shown in FIG. 23, the release holding state of each pole 33 by each control hole 56b of the control plate 56 is released, and the control plate 56 (rotation transmission plate 36) urges the torsion spring 37 against the rotation plate 31. With the movement of returning to the neutral position by the action, their engaging ends 33c are made to mesh with the internal teeth 34 of the base 23. As a result, the output shaft 22 that rotates integrally with the rotating plate 31 is returned to a state in which the rotation is stopped with respect to the base 23. Further, when the operation handle 20 is returned to the neutral position, as shown in FIG. 16, each clutch portion 57a is returned from the riding surface 53g of the inner lever 53 to the relief surface 53f, and is in a friction suppressing state. It becomes P1.

<Action of rotation control device 21 (pulling up operation handle 20)>
24 to 26 show a state in which the operation handle 20 is pulled up from the neutral position. At this time, as shown in FIG. 24, the inner lever 53 is rotated in the direction of the arrow by the rotation of the outer lever 41. As a result, each feed claw 52 is moved in the same direction. Therefore, the engaging end portion 52a forming the outer teeth of the feed claw 52 on the rear side transmits a force to the inner teeth 51 of the rotation transmission plate 36, and pushes the rotation transmission plate 36 in the direction of the arrow. At this time, the engaging end portion 52a forming the outer teeth of the feed claw 52 on the front side is in a state of not meshing with the inner teeth 51 of the rotation transmission plate 36. That is, as the rotation transmission plate 36 rotates, the feed claw 52 on the front side rides on the riding portion 24c on the same side, and the engaging end portion 52a is separated from the meshing with the internal teeth 51.

When the inner lever 53 is rotated as described above, each clutch portion 57a slides on the relief surface 53f of the inner lever 53 and is held in the friction suppressing state P1. Then, due to the rotation of the rotation transmission plate 36, as shown in FIG. 25, the control hole 56b of the control plate 56 integrally with the rotation transmission plate 36 engages with the pins 32b of the two poles 32 at diagonal positions. Then, while leaving the engaging ends 33c of the two poles 33 at other diagonal positions in the state of being meshed with the internal teeth 34 of the base 23, the engaging ends 32c of the two poles 32 are used as the base 23. It is pushed inward in the radial direction so as to be disengaged from the internal teeth 34 of the.

As a result, the locked state of the rotating plate 31 in the upward rotation direction is released. After that, when each protrusion 31d of the rotating plate 31 comes into contact with the end of each engaging elongated hole 56c of the control plate 56, the rotation of the rotation transmitting plate 36 is transmitted to the rotating plate 31. Therefore, as shown in FIG. 26, the rotary plate 31 is fed and rotated with respect to the base 23 in the counterclockwise direction shown in which the rotation transmission plate 36 is fed and rotated, so that the output shaft 22 integrally with the rotating plate 31 is formed. It can be fed and rotated integrally in the direction. At this time, the engaging ends 33c of the two poles 33 at other diagonal positions are prevented from engaging with the internal teeth 34 of the base 23. That is, in this state, the tooth of the engaging end portion 33c receives the load in the normal direction of the tooth of the internal tooth 34 and is moved in the meshing release direction. Therefore, when the rotating plate 31 rotates, the engaging end portions 33c of the two poles 33 slide so as to slide on the internal teeth 34 of the base 23.

When the feed rotation of the rotation plate 31 by the rotation transmission plate 36 is stopped and the operation handle 20 is returned to the neutral position as shown in FIG. 27, the two poles 32 in the diagonal positions that have been released are stopped. As shown in FIG. 28, the release holding state of each pole 32 by each control hole 56b of the control plate 56 is released, and the control plate 56 (rotation transmission plate 36) urges the torsion spring 37 against the rotation plate 31. With the movement of returning to the neutral position by the action, their engaging ends 32c are made to mesh with the internal teeth 34 of the base 23. As a result, the output shaft 22 integrally with the rotating plate 31 is returned to a state in which the rotation is stopped with respect to the base 23.

As shown in FIG. 17, the poles 32 and 33 described above have pins 32b and 33b when their engaging ends 32c and 33c are engaged with the internal teeth 34 of the base 23, respectively. , Each pole 32, 33 is located in the middle portion in the radial direction (radial direction) between the protrusion 31e, which is the center of rotation with respect to the rotating plate 31, and the tip of the internal tooth 34. Therefore, the poles 32 and 33 can be efficiently rotated inward in the radial direction with respect to the amount of rotational movement of the rotation transmission plate 36, and can be disengaged from the meshing with the internal teeth 34 of the base 23 ( (See FIGS. 20 and 25). Therefore, the stroke required for the unlocking operation of the poles 32 and 33 accompanying the operation of the operation handle 20 can be shortened.

<Action of rotation control device 21>
As described above, when the operation handle 20 is pushed down, the seat 1 is lowered by the amount of movement corresponding to the operation. The seat 1 can be adjusted to a desired height by repeating the pressing operation. On the contrary, when the operation handle 20 is pulled up, the seat 1 is similarly raised by the amount of movement corresponding to the operation. The seat 1 can be adjusted to a desired height by repeating the pulling operation. When the sheet 1 reaches the lower limit position or the upper limit position by the above operation, further rotation of the output shaft 22 is stopped as shown in FIG. 32 or FIG. 33.

<Second embodiment>
40 to 43 show a second embodiment of the present invention. The feature of the second embodiment with respect to the first embodiment is that the configuration of the friction generating portion 57 of the rotation control device 21, particularly the configuration of the clutch portion 57a (157a) is changed. The other configurations are the same for both, and the same part will not be described again. Note that FIG. 40 shows only the parts modified with respect to the first embodiment in the second embodiment. Further, in FIGS. 42 and 44, the inner lever 153 shows only the outer shape changed with respect to the first embodiment in the second embodiment, and the description of other shapes is omitted.

As shown in FIGS. 40 to 43, the guide member 157c has a circular ring shape, and engaging protrusions 157c1 are formed at three places on the right peripheral surface thereof at equal intervals. The engaging projection 157c1 is fitted into the through hole 124f of the cover 124 to fix the guide member 157c so as not to move in any direction other than the thrust direction. On the left side surface of the guide member 157c, on the side opposite to the surface on which the engaging projection 157c1 is formed, a pressing surface 157c2 for pressing the leaf spring 57b is formed in three places. The pressing surface 157c2 is formed so as to project to the left from the general surface of the guide member 157c.

On the right side surface of the guide member 157c, a clutch portion 157a is provided adjacent to each of the three engaging protrusions 157c1. As shown in an enlarged manner in FIG. 41, the clutch portion 157a is a member rotatably placed around one end on the right side surface of the guide member 157c along the ring shape of the guide member 157c, and serves as a rotation center. A protrusion 157a1 is formed at one end so as to project to the right. Further, as shown by the solid line in FIG. 41 (indicating a state in which the clutch portion 157a is separated from the guide member 157c), the other end (rotating end portion) of the clutch portion 157a is contacted toward the right side surface of the guide member 157c. The contact surface 157a3 is formed. Like the engaging protrusion 157c1, the protrusion 157a1 is fitted into the through hole 124f of the cover 124, and the clutch portion 157a is rotatably supported around the protrusion 157a1. A spiral surface 157c3 is formed on the right side surface of the guide member 157c at a portion where the contact surface 157a3 of the clutch portion 157a abuts. The spiral surface 157c3 is a spiral surface centered on the axis of the rotation axis (projection 157a1) of the clutch portion 157a. The spiral surface 157c3 has a shape that continuously bulges to the right from the inner peripheral side to the outer peripheral side of the guide member 157c. Further, a protruding portion 157a2 is formed on the inner peripheral side of the contact surface 157a3 of the clutch portion 157a, and the protruding portion 157a2 is a guide member 157c when the clutch portion 157a is placed along the ring shape of the guide member 157c. It is designed to protrude toward the inner circumference of the ring shape.

As shown in FIGS. 42 and 43, there is an inner lever 153 on the inner peripheral side of the guide member 157c, and three riding surfaces 153g in the circumferential direction are formed on the outer periphery of the inner lever 153 so as to project outward in the radial direction. ing. The riding surface 153g of the inner lever 153 is arranged adjacent to the clutch portion 157a of the guide member 157c in the circumferential direction of the guide member 157c. Therefore, as shown in FIG. 44, when the inner lever 153 is rotated in the downward direction (arrow direction) of the seat 1, the protruding portion 157a2 of the clutch portion 157a is radially outside the guide member 157c due to the outer peripheral surface of the riding surface 153g. Is pressed as shown by the arrow. Therefore, the guide member 157c is moved in the thrust direction of the output shaft 22 by the relative movement of the contact surface 157a3 with respect to the spiral surface 157c3, and functions so as to be pressed against the leaf spring 57b. As a result, the friction generating portion 57 is in the friction-on state P2.

According to the friction generating portion 57 of the second embodiment, since the movement locus of the clutch portion 157a is determined to be a rotational movement centered on the axis of the protrusion 157a1, the clutch portion 157a moves excessively during movement. There is no need to do this, and frictional resistance during movement is reduced. Therefore, there is an effect that the operating force for rotating the inner lever 153 is reduced.

<Summary>
Summarizing the above, the lifter device 10 according to the first embodiment has the following configuration. That is, it is a lifter device (10) provided with an output shaft (22) that rotates by receiving rotational power transmitted from the operation handle (20) to raise and lower the seat (1). The lifter device (10) includes a support member (S) that rotatably supports the output shaft (22) and an input member (S) that is coupled to the operation handle (20) and is rotated around the axis of the output shaft (22). N), the feed unit (A) that transmits the forward and reverse bidirectional rotation of the input member (N) to the output shaft (22), and the rotation of the output shaft (22) are locked with respect to the support member (S). It has a lock portion (B) and a friction generating portion (57) that applies a frictional force to the rotation of the output shaft (22).

The friction generating portion (57) is supported by an elastic body (57b) provided between the output shaft (22) and the support member (S), a rotary cam (53) connected to the input member (N), and a support. The elastic body (57b) is supported by the member (S) and pushed in the radial direction by the rotation of the rotary cam (53) to rotate the elastic body (57b) integrally with the output shaft (22) in the thrust direction. It has a clutch portion (57a) that is pressed against the surface to generate friction. The rotary cam (53) does not push the clutch portion (57a) in the radial direction even when the operation handle (20) is in the neutral position and is turned in the direction of raising the seat (1) from the neutral position. The friction suppression state (P1) that suppresses the generation of friction due to (57b) is set, but the clutch portion (57a) is rotated by turning the operation handle (20) in the direction of lowering the seat (1) from the neutral position. The switching structure is set to a friction-on state (P2) in which friction is generated by the elastic body (57b) by pushing in the direction.

According to the above configuration, when the operation handle (20) is not operated and when the seat (1) is operated in the raising direction, the friction generating portion (57) is set to the friction suppressing state (P1). Therefore, the operating load when the seat (1) is raised by the operating handle (20) does not become heavy. Further, when the operation handle (20) is returned to the neutral position, the lock portion (B) can be smoothly locked without being affected by friction. On the other hand, when the operation handle (20) is operated in the direction of lowering the seat (1), the friction generating portion (57) is set to the friction on state (P2). Therefore, it is possible to appropriately prevent the output shaft (22) from sliding and rotating due to the action of its own weight applied to the seat (1). Further, since the clutch portion (57a) presses the elastic body (57b) between the elastic body (57b) and the rotating member (31) in the thrust direction, the rotation of the operation handle (20) when it is returned to the neutral position is less likely to be hindered.

Further, the lock portion (B) has a release structure in which the operation handle (20) is released from the lock with the support member (S) by being rotated by a predetermined amount in each of the forward and reverse directions from the neutral position. The rotary cam (53) pushes the clutch portion (57a) in the radial direction by rotation until the operation handle (20) is rotated by a predetermined amount to switch to the friction-on state (P2). According to the above configuration, when the operation handle (20) is operated in the direction of lowering the seat (1) to unlock the lock portion (B), the friction generating portion (57) is always in the friction-on state (P2). ). Therefore, it is possible to more appropriately prevent the output shaft (22) from sliding and rotating due to the action of its own weight applied to the seat (1).

Further, the surface that supports the clutch portion (57a) with respect to the support member (S) supports the clutch portion (57a) as the rotary cam (53) moves in the radial direction of the clutch portion (57a). ) Is an inclined surface (57c2) that guides the vehicle so as to move it diagonally in the thrust direction. According to the above configuration, the clutch portion (57a) is in a friction-on state (P2) and a friction suppression state (P1) in response to a movement in which the operation handle (20) is turned in both forward and reverse directions and returned to the neutral position. ) And can be switched smoothly.

Further, the member that supports the clutch portion (157a) with respect to the support member (S) is composed of a guide member (157c) that is supported so as to be movable only in the thrust direction with respect to the support member (S). The clutch portion (157a) is rotatably supported on the guide member (157c) in the radial direction, and the rotating end portion of the clutch portion (157a) and the support surface on the guide member (157c) with respect to the rotating end portion are eventually supported. One is a spiral surface (157c3) centered on the rotation center of the clutch portion (157a), and one of the other slides in contact with the spiral surface (157c3) as the clutch portion (157a) rotates. The contact surface (157a3) is formed, and the rotating end of the clutch (157a) is pushed in the radial direction by the rotating cam (153) to rotate the clutch (157a) and guide member (157c). The elastic body (57b) is configured to be pressed in the thrust direction. According to the above configuration, since the movement locus of the clutch portion (157a) is a rotational movement in which the center of rotation is determined, the clutch portion (157a) does not make any extra movement during movement, and the clutch portion (157a) does not move excessively during movement. Friction resistance is reduced. Therefore, there is an effect that the operating force for rotating the rotary cam (153) is reduced.

Further, the member that supports the clutch portion (57a) with respect to the support member (S) is composed of a guide member (57c) that is supported so as to be movable only in the thrust direction with respect to the support member (S). The clutch portion (57a) is pushed in the radial direction by the rotary cam (53) and is pushed in the thrust direction between the support member (S) and the guide member (57c), and is elastic by the guide member (57c). Press the body (57b) in the thrust direction. The guide member (57c) has a gap (T) in the thrust direction between the guide member (57c) and the support member (S) with the clutch portion (57a) in between in the friction suppression state (P1). According to the above configuration, the support member (S) and the guide member (57c) are less likely to come into direct contact with each other, so that it is possible to suppress the generation of abnormal noise due to contact between the two.

Further, the elastic body (57b) is coupled to the guide member (57c) in a state of being integrated in the rotational direction. According to the above configuration, the frictional resistance exerted by the elastic body (57b) is less likely to fluctuate, so that the operation feeling of the operation handle (20) can be kept constant.

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

1. 1. The lifter device of the present invention can be widely applied not only to seats applied to vehicles other than automobiles such as railways, but also to seats used for various vehicles such as aircraft and ships. Further, the lifter device of the present invention can be widely applied to seats for non-vehicles installed in facilities such as movie theaters.

2. 2. The elastic body constituting the friction generating portion does not necessarily have to be made of an annular member, but may be made of pieces (small pieces) dispersed in one place or a plurality of places in the rotation direction. Further, the elastic body may be made of a material other than metal such as rubber or resin. Further, the elastic body may be attached to the guide member when there is a guide member for supporting the clutch portion, but is attached to the support member or the rotating member that rotates integrally with the output shaft. You may.

3. 3. The clutch portion is indirectly supported by the support member by a guide member supported so as to be movable only in the thrust direction with respect to the support member, and is directly supported by the support member. It may be configured. The clutch portion may be provided at one location, two locations, or four or more locations in the rotation direction.

In the second embodiment, the guide member is provided with a spiral surface and the rotating end of the clutch portion is provided with a contact surface. On the contrary, the guide member is provided with a contact surface and the rotating end portion of the clutch portion is provided with a spiral surface. May be provided. In this case, the spiral surface at the rotating end of the clutch portion has a shape that continuously bulges from the outer peripheral side to the inner peripheral side of the guide member toward the contact surface of the guide member.

4. The friction suppressing state of the friction generating portion may be a state in which friction is generated smaller than the friction on state or a state in which friction is not generated.

1 Seat 2 Seat Cushion 3 Seat Back 4 Floor 5 Lower Rail 6 Upper Rail 7 Bracket 8 Seat Slide Device 10 Lifter Device 11 Link Member 11a Front Link 11b Rear Link 12 Link Mechanism 13 Side Frame 13a Through Hole 14 Support Bracket 16 Sector Gear 17 Torque Rod 18 Pinion gear 20 Operation handle 21 Rotation control device 22 Output shaft 22a Outer peripheral surface 22b Spline 22c End 23 Base 23a Through hole 23b Guide recess 23c Center hole 23d Engagement groove 24 Cover 24a Through hole 24b Engagement piece 24c Riding part 24d Leg 24e Through hole 24f Engagement hole 31 Rotating plate (rotating member)
31a Sliding surface 31b Spline hole 31c Long hole 31d, 31e Protrusion 31f First engagement pin 31g Second engagement pin 32, 33 Pole 32a, 33a Through hole 32b, 33b Pin 32c, 33c Engagement end 34 Internal tooth 35 Torsion spring 35a Winding part 35b End part 36 Rotation transmission plate 36a Spline fitting part 36c Long hole 36d Center hole 37 Torsion spring 37a End part 41 Outer lever 41a Through hole 41b Center hole 42 Engagement piece 43 Torsion spring 43a End part 51 Tooth 52 Feed claw 52a Engagement end 52b Hinge 53, 153 Inner lever (rotary cam)
53a Stopper pin 53b Through hole 53d Center hole 53e Facing part 53f Relief surface 53g, 153g Riding surface 53h Inclined surface 54 Temporary holding member 54a Feed claw holding part 54a1 Rotating receiving surface 54b Shaft support 54c Spacer part 55 Torsion spring 55a End 56 Control plate 56a Spline hole 56b Control hole 56c Engagement slot 57 Friction generating part 57a, 157a Clutch part 157a1 Protrusion 157a2 Protruding part 157a3 Contact surface 57b Leaf spring (elastic body)
57b1 Locking claw 57c, 157c Guide member 57c1, 157c1 Engagement protrusion 57c2 Inclined concave surface (inclined surface)
57c3 Flange 57c4 Locking hole 157c2 Pressing surface 157c3 Spiral surface 57d Rotating ring 57d1 First engaging hole 57d2 Second engaging hole 57e Fixing ring 57e1 Engaging claw 60 Stopper 61 Support member side protrusion 62 Engaging piece 63 Rotating shaft Side protrusion S Support member A Feed part B Lock part N Input member P1 Friction suppression state P2 Friction on state T Gap

Claims (6)

It is a lifter device equipped with an output shaft that rotates by receiving rotational power from the operation handle and raises and lowers the seat.
A support member that rotatably supports the output shaft and
An input member that is coupled to the operation handle and is rotated around the axis of the output shaft.
A feed unit that transmits the forward / reverse bidirectional rotation of the input member to the output shaft, and
A lock portion that locks the rotation of the output shaft with respect to the support member,
It has a friction generating part that applies a frictional force to the rotation of the output shaft.
The friction generating portion is supported by an elastic body provided between the output shaft and the support member, a rotary cam connected to the input member, and the support member in the radial direction due to the rotation of the rotary cam. It has a clutch portion that is pushed and presses the elastic body in the thrust direction between the rotating member that rotates integrally with the output shaft to generate friction, and the rotating cam has the operation handle neutral. The clutch portion is not pushed in the radial direction even when the clutch portion is rotated in the direction of raising the seat from the position and the neutral position, and the friction suppression state is set in which the generation of friction by the elastic body is suppressed. A lifter device having a switching structure in which the clutch portion is pushed in the radial direction by turning the handle in the direction of lowering the seat from the neutral position to generate friction by the elastic body. The lifter device according to claim 1.
The lock portion has a release structure in which the operation handle is released from the lock with the support member by being rotated by a predetermined amount in each of the forward and reverse directions from the neutral position.
A lifter device in which the rotary cam pushes the clutch portion in the radial direction by rotation until the operation handle is rotated by the predetermined amount to switch to the friction-on state. The lifter device according to claim 1 or 2.
The surface that supports the clutch portion with respect to the support member guides the clutch portion obliquely in the thrust direction with respect to the support member as the clutch portion moves in the radial direction by the rotary cam. A lifter device that is considered to be an inclined surface. The lifter device according to claim 1 or 2.
The member that supports the clutch portion with respect to the support member is composed of a ring-shaped guide member supported so as to be movable only in the thrust direction with respect to the support member.
The clutch portion is rotatably supported on the guide member in the radial direction, and one of the rotating end portion of the clutch portion and the support surface on the guide member with respect to the rotating end portion is the rotation of the clutch portion. A spiral surface centered on the center, one of which is a contact surface that abuts and slides against the spiral surface as the clutch portion rotates, and the rotating end of the clutch portion rotates. A lifter device configured to rotate the clutch portion by being pushed in the radial direction by a cam and press the elastic body in the thrust direction by the guide member. The lifter device according to any one of claims 1 to 3.
The member that supports the clutch portion with respect to the support member is composed of a guide member supported so as to be movable only in the thrust direction with respect to the support member.
The clutch portion is pushed in the thrust direction between the support member and the guide member by being pushed in the radial direction by the rotary cam, and the elastic body is pushed in the thrust direction by the guide member.
A lifter device in which the guide member has a gap in the thrust direction between the guide member and the support member via the clutch portion in the friction suppressing state. The lifter device according to claim 5.
A lifter device in which the elastic body is coupled to the guide member in a state of being integrated in the rotational direction.

Images