JP2003320879A - Transmission mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission mechanism in which a loss of operation amount of a handle is made less. <P>SOLUTION: The transmission mechanism comprises a brake mechanism 9 in which torsion springs 45A, 45B provided with hook parts at both ends are arranged in a stopper case 42 so as to butt to an inner wall of the stopper case 42, a core 43 of a shaft 21 side provided with notch is rotatably inserted to inner walls of the torsion springs 45A, 45B and a claw part 46A of a stopper plate 46 integrally formed with a ratchet (rotation body) 6 is inserted into a notch space of the core 43; and a ratchet mechanism for rotating the shaft 21 of the brake mechanism 9 in one direction by reciprocating the handle 3 urged so as to be positioned at a neutral position from the neutral position to one direction. A spacer (resistance means) 100 for inhibiting a self-rotation of the shaft 21 is provided and when the handle 3 is returned to the neutral position, it overwhelms shaft-returning force applied to the shaft 21. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention provides a torsion spring having hooks at both ends arranged in a stopper case so as to abut an inner wall of the stopper case, and a shaft-side core having a notch formed therein. The brake mechanism was rotatably inserted into the inner wall of the spring, and the claw portion of the stopper plate integrally formed with the pinion was inserted into the space of the notch of the core, and was biased to be positioned in the neutral position. The present invention relates to a transmission mechanism including a ratchet mechanism that rotates a shaft of the brake mechanism in the one direction by reciprocating a handle in the one direction from the neutral position.

[0002]

2. Description of the Related Art A lifter mechanism for raising and lowering a seat cushion of a seat, a vertical mechanism for raising and lowering only a front portion or a rear portion of the seat cushion, a tilt mechanism for tilting the seat cushion, etc. are transmission mechanisms having a brake mechanism.

An example of the brake mechanism is shown in FIGS. 15 and 16. In the drawing, a torsion spring 202 is arranged in the stopper case 201 so as to press the inner wall of the stopper case 201,
A core 203 having a notch 203a formed therein is rotatably inserted inside the torsion spring 202.
The core 203 is integrally fixed to the shaft 204. Further, in the space of the notch 203a of the core 203, the hook portion 202a of the torsion spring 202,
A claw portion 205a of a stopper plate 205, which is integrally formed with the pinion 206, is inserted between 202b so as to be rotatable around a shaft 204.

Therefore, with respect to the rotational force from the pinion 206 side, the side end portion 205b or the side end portion 205c of the claw portion 205a is hooked on the hook portion 20 of the torsion spring 202.
2a or the hook portion 202b is pushed to act to widen the outer diameter of the torsion spring 202, so that the pressure contact force between the torsion spring 202 and the stopper case 201 becomes strong, and the rotation of the pinion 206 is blocked. On the other hand, with respect to the rotational force from the shaft 204 side, the hook portion 202 a of the torsion spring 202 or the hook portion 202.
Since b receives a force in the direction of contracting the outer diameter from the side end portion 203b or the side end portion 203c of the core 203, the pressure contact force becomes small and the shaft 204 can rotate, and the torsion spring 202 and the claw portion 205a are used. Te Pinion 206
Can be rotated.

[0005]

By the way, in the brake mechanism, in the natural state, the side end portions 203b and 203b of the core 203 are arranged so that the braking force can be surely obtained against the input from the pinion 206 side. 203c, the hook portion 202a of the torsion spring 202, and the hook portion 20.
It is set so that gaps S and S'will always exist between 2b and 2b.

Therefore, the shaft 204 has a play in the rotational direction. There are the following two mechanisms as a mechanism for rotating the shaft 204. (1) A mechanism in which a handle is directly fixed to the shaft 204 and the shaft 204 is rotated by rotating the handle. (2) The handle is provided via a ratchet mechanism having an axis side ratchet wheel and a handle side pole,
A mechanism for rotating the shaft 204 in one direction by reciprocating the handle in the neutral position in one direction by the biasing means.

Here, in the mechanism in which the handle is directly fixed to the shaft 204, the backlash in the rotating direction of the shaft 204 affects only the start of rotation of the handle, and the loss of the handle operation amount is not so large.

However, in the mechanism in which the handle is provided via the ratchet mechanism consisting of the ratchet wheel and the pole, when the force for rotating the handle is released,
The pole slides on the ratchet wheel and only the handle returns. At this time, when the pole slides on the ratchet wheel, an axial returning force acts on the ratchet wheel (shaft) to rotate the ratchet wheel, and the side ends 203b and 203c of the core 203 are rotated.
And the hook portion 202a of the torsion spring 202,
Clearances S and S ′ are always generated between the hooks 202b. That is, each time the handle is returned to the neutral position, backlash occurs in the rotation direction of the shaft 204, resulting in a large loss of the handle operation amount.

The present invention has been made in view of the above problems, and an object thereof is to provide a transmission mechanism in which the loss of the steering wheel operation amount is small.

[0010]

According to a first aspect of the invention for solving the above-mentioned problems, a torsion spring having hook portions at both ends is arranged in a stopper case so as to abut against an inner wall of the stopper case, and a notch is formed. A brake mechanism in which the engraved shaft side core is rotatably inserted into the inner wall of the torsion spring, and a claw portion of a stopper plate integrally formed with the rotating body is inserted into a space of the notch of the core. , A braking mechanism that has a ratchet and an engaging member that engages with ratchet teeth of the ratchet, and is reciprocated from the neutral position in one direction from the neutral position by urging the handle to be biased to the neutral position. In a transmission mechanism including a ratchet mechanism that rotates the shaft of the brake mechanism in one direction, a resistance unit that applies a resistance force to the rotation of the shaft of the brake mechanism is provided. When the handle returns to the neutral position, a sliding mechanism between the ratchet teeth of the ratchet of the ratchet mechanism and a front engaging member causes a shaft return force acting on the shaft to be overcome. Is.

A resistance means is provided for applying a resistance force to the rotation of the shaft of the brake mechanism, and when the handle returns to the neutral position, the ratchet teeth of the ratchet of the ratchet mechanism and the engaging member slide to cause the shaft to slip. Since the shaft return force acting on the shaft is overcome, even if the handle is returned to the neutral position, there is no backlash in the rotation direction of the shaft. Therefore, the loss of the steering wheel operation amount is reduced.

According to a second aspect of the present invention, the resistance means is
The transmission mechanism according to claim 1, wherein the spacer is a spacer that comes into contact with the inner wall of the stopper case and the core. A desired resistance value can be obtained by changing the material and thickness of the spacer that comes into contact with the inner wall of the stopper case and the core, and the area that comes into contact with the inner wall of the stopper case and the core.

According to a third aspect of the present invention, the resistance means is
The transmission mechanism according to claim 1, wherein the transmission mechanism is a protrusion formed on at least one of the stopper case and the core and abutting against the other.

Since the resistance means is a projection formed on at least one of the stopper case and the core and abutting against the other, cost reduction can be achieved.

According to a fourth aspect of the present invention, the resistance means is
The transmission mechanism according to claim 1, wherein the transmission mechanism is provided on a bearing portion that rotatably supports the shaft. A desired resistance value can be obtained by changing the contact area between the bearing portion and the shaft, the contact pressure, and the material of the bearing portion and the shaft.

A burring hole is an example of the bearing.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment in which the transmission mechanism of the present invention is applied to a seat lifter will be described below with reference to the drawings.

FIG. 1 is a side view showing an outline of a seat arranged in a passenger compartment of an automobile. The seat shown here has a seat cushion 1 that supports the back of the seated person, and a seat back 2 that supports the back of the seated person. The seat cushion 1 has a seat cushion frame that forms the framework thereof. By rotating the handle 3 of the seat lifter, its height can be adjusted as described later.

The seat cushion 1 has a seat track 4
The seat track 4 is supported by a floor panel 5 of the vehicle body via a lower rail 4A fixed to the floor panel 5 and an upper rail slidably mounted in the longitudinal direction along the lower rail 4A. 4B and
The seat cushion 1 is supported on the upper rails 4B as described later. Upper rail 4B to lower rail 4
By sliding with respect to A, the seat cushion 1
Can be adjusted in the front-back direction (left-right direction in FIG. 1). The seat cushion 1 may be directly fixed to and supported by the floor panel 5 without using the seat track 4.

2 to 4 show the handle 3 shown in FIG.
FIG. 3 is a side view showing a pinion 6 rotatably driven by the rotation of the pinion 6, an example of a transmission unit that converts the rotation of the pinion 6 into a lifting operation of the seat cushion 1, and a lifter support body 8. , The handle 3 and a transmission mechanism described later for transmitting the rotation thereof to the pinion 6 are omitted. Further, most of the transmission means shown in FIGS. 2 to 4, the lifter support body 8, the pinion 6, and the transmission mechanism for transmitting the rotation of the handle 3 to the pinion 6 are covered by a cover (not shown). The handle 3 is exposed to the outside of the cover as shown in FIG.

The lifter support 8 shown in FIGS. 2 to 4 is
It is made of a rigid body such as a metal plate or a hard resin plate, and the lifter support body 8 constitutes a part of the seat cushion frame. The pinion 6 is rotatably supported by the lifter support 8 via elements described later.

A sector gear-shaped rack 11 that meshes with the pinion 6 is rotatably supported on the lifter support 8 via a support shaft 10. Further, on the upper rail 4B of the seat track 4 shown in FIG. 1, the base end sides of the first and second support links 12 and 13 are rotatably supported via pins 14 and 15, respectively. 12,
The free end side of 13 is rotatably connected to the lifter support 8 via pins 16 and 17. Further, the rack 11 and the second support link 13 described above are rotatably connected to respective ends of a connection link 20 via pins 18 and 19.

FIG. 2 shows a state in which the seat cushion 1 occupies an intermediate position in the vertical direction, FIG. 3 shows the seat cushion 1 at the uppermost position, and FIG. 4 shows the seat cushion 1 at the lowermost position. It shows the situation when occupying each.

The handle 3 shown in FIG. 1 has a base portion 3A.
And a handle portion 3B extending from the base portion 3A in the radial direction thereof, the handle portion 3 is formed by a seated person.
The handle 3 can be rotated by grasping B.
Now, assuming that the seat cushion 1 is at the intermediate position shown in FIG. 2, and the handle 3 is rotated in the first direction (clockwise direction indicated by arrow A in the example of FIG. 1) in this state, the rotation will be described later. To the pinion 6, and the pinion 6 also rotates in the first direction A (clockwise direction in FIG. 2). Therefore, the rack 11 rotates counterclockwise in FIG. 2 about the support shaft 10 and moves the connecting link 20 leftward in FIG. As a result, the first and second support links 12 and 13 rotate counterclockwise about their respective base end sides, and as shown in FIG.
The lifter support 8 connected to the terminals 2 and 13, that is, the seat cushion 1 as a whole rises.

On the other hand, when the seat cushion 1 is in the intermediate position shown in FIG. 2, the handle 3 shown in FIG. 1 is moved in the second direction (arrow B in the example of FIG. 1) opposite to the first direction. When rotated in the counterclockwise direction (shown), the pinion 6 shown in FIG. 2 also rotates in the second direction B, that is, the counterclockwise direction.
As a result, the rack 11 rotates about the support shaft 10 in the clockwise direction in FIG. 2, and the connecting link 20 moves to the right in FIG. As a result, the first and second support links 12 and 13 rotate clockwise around the base ends thereof, whereby the seat cushion 1 descends as shown in FIG.

2 to 4 show the structure of one side portion of the seat cushion 1 in the width direction (direction perpendicular to the paper surface of FIGS. 1 to 4), the other side portion also has a lifter. Support, rotating body that rotates in the same manner as the rack 11, first
And a second support link, and the second support link and a connecting link in which each end is pivotally attached to the rotating body. The rack 11 is fixed to one end of the support shaft 10,
The supporting shaft 10 is rotatably supported by the lifter supporting member 8 and the other side lifter supporting member and extends long in the width direction of the seat cushion 1, and the rotating body is fixed to the other end of the supporting shaft 10. Has been done. Therefore, by rotating the pinion 6 as described above, the rotating body on the other side of the seat cushion 1, the connecting link, and the first and second links are
The rack 11 and the connection link 20 shown in FIGS. 2 to 4.
Then, the same operation as the first and second links 12 and 13 is performed, whereby the seat cushion 1 can be raised or lowered in a stable state.

As described above, the first and second support links, the rack, the rotating body, the support shaft, and the connecting link constitute an example of a transmission means for converting the rotation of the pinion 6 into the lifting operation of the seat cushion 1. ing.

Transmission means other than the illustrated form can be adopted as appropriate. Further, in the seat lifter shown in FIGS. 2 to 4, the seat cushion 1 is moved up and down by the rotation of the pinion 6. However, a rotating body other than the pinion is used, and the rotation of the rotating body is used to move the seat cushion 1 up and down. It can also be configured to convert to. As described above, the seat lifter of this example includes the lifter support body 8, the handle 3, the pinion 6 that is an example of the rotating body, and a unit that converts the rotation of the rotating body into the lifting operation of the seat cushion 1. ing.

FIG. 5 is a sectional view showing an example of the handle 3 and a transmission mechanism for transmitting the rotation thereof to the pinion 6.
Is an exploded sectional view thereof. Further, FIG. 7 shows the transmission mechanism as shown in FIG.
It is a figure seen from the right side of, with some elements omitted,
8 is a diagram showing the handle 3 by a chain line, and FIG. 8 is a diagram showing each of some elements of the transmission mechanism.

As can be seen from FIGS. 5 and 6, the seat lifter has a shaft 21, which is provided with a support piece 8A fixed to the lifter support 8 and a brake mechanism 9 described in detail later. And is rotatably supported by the lifter support 8. A handle joint bracket 22 and a handle bracket 23 are fixed to the handle 3 by a plurality of screws 24. The handle joint bracket 22 and the handle bracket 23 are made of a plate material, and the center hole 25 of the handle bracket 23 is rotatably fitted to the shaft 21. In this way, the handle 3
It is supported by the shaft 21 via a handle joint bracket 22 and a handle bracket 23 so as to be rotatable relative to the shaft 21. The handle joint bracket 22 and the handle bracket 23 may be omitted, and the handle 3 may be directly rotatably supported on the shaft 21. The handle 3 and the shaft 21 rotate about their common axis of rotation X.

A ratchet wheel 26 arranged concentrically with the shaft 21 is fixed to the shaft 21, and the pinion 6 which is an example of the rotating body shown in FIGS. 2 to 4 is, as shown in FIG. It is arranged concentrically with the shaft 21. Further, the brake mechanism 9 allows the rotation of the shaft 21 to be transmitted to the rotating body composed of the pinion 6, but the rotating body is rotated when a rotational force is applied to the rotating body from outside the shaft. And the specific configuration thereof will be described later in detail.

The seat lifter further has a guide member 27 made of a thin plate. The guide member 27 has a pair of arms 27A as shown in FIGS. 7 and 8, and each arm 27A is illustrated. It is fixedly fixed to the lifter support body 8 by a screw that is not provided,
Shaft 21 is inserted in. As shown in FIGS. 7 and 8, the guide member 27 is formed with an arc-shaped elongated hole 29 centered on the rotation axis X of the handle 3, and the elongated hole 29 has first and second poles 29 formed therein. First and second pole support members 31A and 31 supporting 30A and 30B, respectively
B is slidably fitted along the elongated hole 29. The pole support members 31A and 31B of this example are formed of pins, and their respective tip portions are fitted into the holes 32A and 32B (FIG. 8) formed in the handle bracket 23 as shown in FIGS. 5 and 6. , Fixed here. The holes 33A and 33B (FIG. 8) formed in the first and second poles 30A and 30B are rotatably fitted to the first and second pole support members 31A and 31B. . In this way, the poles 30A and 30B are swingably supported by the pole support members 31A and 31B, and the swing axis lines Y1 and Y2 that are the swing centers at this time are the pole support members 31A and 31B. It becomes the central axis of.

As described above, the first and second pole support members 31A and 31B are fixed to the handle 3 via the handle bracket 23.
1A and 31B may be directly fixed to the handle 3, or the first and second poles 30A and 30B may be directly swingably supported on the handle 3 without the pole support members 31A and 31B. Good. In either case, as shown in FIG. 7, the first and second pawls 30A and 30B have their swing axes Y1 and Y2 located at a distance L1 from the rotation axis X of the handle 3 in the radial direction. Therefore, when the handle 3 rotates, the first and second pawls 30A and 30B revolve around the rotation axis X which is the center of rotation. Moreover, the first and second poles 30A and 30B
Are supported by the handle 3 via other elements (or directly) so as to be swingable about their own swing axes Y1 and Y2.

As shown in FIG. 7, the claws 34A and 34B of the first and second pawls 30A and 30B (engaging members) are respectively formed.
Can be engaged with teeth (ratchet teeth) 35 on the circumferential surface of the ratchet wheel 26 at different positions in the circumferential direction of the ratchet wheel 26.

Further, as shown in FIGS. 7 and 8, a cam 36 is formed on the outer peripheral portion of the guide member 27, and the cam 36 has a portion of the outer peripheral portion of the guide member which is adjacent to the guide. It is formed by bulging in the radial direction from the outer peripheral portion of the member. On the other hand, the first and second poles 30
A and 30B have protrusions 37A and 37B that are in sliding contact with the outer peripheral portion of the guide member 27 including the cam 36. Further, in the first and second pawls 30A and 30B, the pawl portions 34A and 34B of the pawls 30A and 30B are securely attached to the teeth 35 of the ratchet wheel 26 by the urging action of the pole pushing spring 38 formed of a leaf spring. Can be engaged with. At that time, the first and second poles 30A, 30B
Are fitted and held in the holding portions 38A and 38B of the spring 38, respectively.

FIG. 7 shows a state in which the handle 3 is in the neutral position. At this time, the first and second poles 3 are shown.
The pawl portions 34A, 34B of the 0A, 30B are both engaged with the teeth 35 of the ratchet wheel 26 by the biasing action of the spring 38.
Is engaged with. Moreover, the protrusions 37A, 37B of the pawls 30A, 30B are in pressure contact with the outer peripheral portion of the guide member adjacent to the cam 36 with the cam 36 sandwiched therebetween.

Here, as described above, when the handle 3 is rotated in the first direction A, that is, the clockwise direction in FIG. 7, in order to raise the seat cushion 1 shown in FIG. 1, the first and second directions are obtained. The poles 30A and 30B revolve around the rotation axis X of the handle 3 in the first direction A. Therefore, the protrusion 37A of the first pole 30A moves in a direction away from the cam 36, and the claw portion 3 of the first pole 30A moves.
4A remains engaged with the teeth 35 of the ratchet wheel 26. On the other hand, the protrusion 37B of the second pole 30B
Rides on the cam 36, so the second pole 30B
7 swings clockwise about the swing axis Y2 in FIG. 7, the pawl portion 34B of the pole 30B separates from the tooth 35 of the ratchet wheel 26, and the engagement between the two is released.

Since the claw portions 34A of the first pole 30A remain engaged with the teeth 35 of the ratchet wheel 26, and the first pole 30A revolves in the first direction A,
The pawl portion 34A rotates the ratchet wheel 26 in the first direction A, that is, the clockwise direction in FIG. 7, while being strongly meshed with the teeth 35 of the ratchet wheel 26. When the ratchet wheel 26 rotates in this way, the shaft 21 fixed to the ratchet wheel 26 also has the same first direction A.
The rotation is transmitted to the pinion 6 via the brake mechanism 9 in a manner described later, and the rotation causes the rotation of FIG.
Also, the seat cushion 1 rises as described above with reference to FIG.

When the handle 3 is rotated in the first direction A by a predetermined angle smaller than 360 °, for example, 20 ° to 30 °, the first pole support member 31A causes the one end 29A of the elongated hole 29 to move. This prevents further rotation of the handle 3. Thus, the end portion 29A of the long hole 29
Serves as a stopper for the pole support member 31A.

Next, when the seated person releases the handle 3, the return spring, which will be described later, acts to cause the handle 3 to move.
Returns to the neutral position shown in FIG. 7 together with the first and second poles 30A and 30B and the first and second pole support members 31A and 31B, and at this time, the claw portions 34B of the second pole 30B also. Engage with teeth 35. Even during this returning operation, the claw portion 34A of the first pole 30A remains engaged with the tooth 35 of the ratchet wheel 26, but at that time, as described later, the claw portion 34A changes the ratchet wheel 26.
The ratchet wheel 26 into the second position
Direction B, that is, the counterclockwise direction in FIG. 7, does not rotate.

Each time the above-described turning operation of the handle 3 (operation of reciprocating the handle 3 in one direction from the neutral position) is performed, the seat cushion 1 is raised by a predetermined amount and the turning operation is performed. By repeating the operation, the seat cushion 1 can be finally lifted to the uppermost position shown in FIG.

When the handle 3 is rotated in the second direction B, that is, the counterclockwise direction in FIG. 7, from the state where the handle 3 is in the neutral position shown in FIG. 7, this time, the first pole 30A moves. Since the protrusion 37A rides on the cam 36, the claw 34A thereof is separated from the tooth 35 of the ratchet wheel 26, and the claw 34B of the second pole 30B meshes with the tooth 35 of the ratchet wheel 26, so that the ratchet wheel 2
6 is rotated in the second direction B (counterclockwise in FIG. 7).
Then, the rotation is transmitted to the pinion 6 via the shaft 21 and the brake mechanism 9, whereby the seat cushion 1 is lowered by a predetermined amount. Also in this case, handle 3
When rotated by a predetermined angle smaller than 60 °, the second pole support member 31B comes into contact with the other end 29B of the elongated hole 29, and further rotation of the handle 3 is prohibited. If the hand is released from the handle 3 in this state, the handle 3 also returns to the neutral position shown in FIG. 7 by the action of the return spring. By rotating the handle 3 again in the second direction B, the seat cushion 1 is lowered by a predetermined amount, and by repeating this operation, the seat cushion 1 is moved to the position shown in FIG.
It can be lowered to the lowest position shown in.

As described above, by rotating the handle 3 in the first or second direction by a predetermined angle smaller than 360 °, the seat cushion 1 can be raised or lowered, and the rotation thereof can be performed. By repeating the operation, the seat cushion 1 can be brought to the uppermost position or the lowermost position. The seat cushion 1 can be raised and lowered to the uppermost position or the lowermost position without turning the handle 3 at a large angle, for example, 360 ° or more. As a result, the seated person can easily perform the operation. In this way, the seated person
It is possible to adjust the seat cushion 1 to a desired height position and to sit in the seat in a comfortable posture.

As can be understood from the above description, the cam 36 moves the handle 3 in the neutral position into the first direction A.
The first and second pawls 30A, 3 that were previously engaged with the teeth 35 of the ratchet wheel 26 when rotated to
The second pole 30B of the claw portions 34A and 34B of 0B
The second pawl 30 so that the claw portion 34B of the second pole 30 is separated from the tooth 35 of the ratchet wheel 26 to release the engagement.
B is swung, and the handle 3 that was in the neutral position is moved to the second position.
The first and second pawls 3 which have been engaged with the teeth 35 of the ratchet wheel 26 when rotated in the direction B of FIG.
Of the claw portions 34A and 34B of 0A and 30B, the claw portion 34A of the first pole 30A is the tooth 3 of the ratchet wheel 26.
The first pole 30A is rocked so that the first pole 30A is separated from the fifth pole 5 and the engagement thereof is released.

FIG. 9 is an explanatory view showing the engaged state of the teeth 35 of the ratchet wheel 26 with the first pole 30A.
The first pole 30A is the tooth 3 of the ratchet wheel 26.
Considering the case of revolving in the first direction A from the position shown in FIG. 7 in the state of being engaged with 5, the claw portions 34A of the first pawl 30A have the teeth 3 of the ratchet wheel 26 at this time.
A vertical force F is applied to 5. Therefore, the claw portion 34A meshes strongly with the tooth 35 to rotate the ratchet wheel 26 in the first direction A. Conversely, the first pole 3
When 0B revolves in the second direction B, its pole 30
Since the claw portion 34A of A slides against the teeth 35 of the ratchet wheel 26 as shown by the arrow C, the ratchet wheel 26 does not rotate in the second direction B nor in the first direction A, and the claw portion 34A does not rotate. 34A can return to the position shown in FIG. 7 while overcoming the teeth 35 of the ratchet wheel 26. The relative position of the swing axis Y1 of the first pawl 30A and the claw portion 34A of the first pawl 30A that engages with the teeth 35 of the ratchet wheel 26 is set so that such an action is obtained. .

Similarly, when the second pole 30B revolves in the second direction B from the position shown in FIG. 7, its claw portion 34B.
Applies a force in the vertical direction to the teeth 35 of the ratchet wheel 26 to rotate the ratchet wheel 26 in the second direction, and conversely the second pole 30B causes the second pole 30B to move in the first direction A.
When it revolves around, the pawl portion 34B moves to the ratchet wheel 2.
The teeth 35 of 6 slide, and the ratchet wheel 26 stops without rotating.

As described above, when the first pawl 30A revolves in the first direction A with the pawl portion 34A of the first pawl 30A engaged with the teeth 35 of the ratchet wheel 26, The pawl portion 34A of the first pole 30A meshes with the tooth 35 of the ratchet wheel 26 to rotate the ratchet wheel 26 in the first direction A, and the pawl portion 34A of the first pole 30A has the tooth 35 of the ratchet wheel 26.
When the first pawl 30A revolves in the second direction B opposite to the first direction A in the state of being engaged with, the pawl portion 34A of the first pawl 30A causes the teeth 35 of the ratchet wheel 26 to move.
In order to prevent the ratchet wheel 26 from rotating by sliding against the rocking axis Y1 of the first pole 30A.
And the relative position of the claw portion 34A of the first pole 30A that engages with the tooth 35 of the ratchet wheel 26 is set.
Similarly, when the second pawl 30B revolves in the second direction B with the pawl portion 34B of the second pawl 30B engaged with the teeth 35 of the ratchet wheel 26, the pawl of the second pawl 30B is The portion 34B is the tooth 3 of the ratchet wheel 26.
5, the ratchet wheel 26 is rotated in the second direction B, and the pawl portion 34B of the second pawl 30B is engaged with the tooth 35 of the ratchet wheel 26. When revolved in the direction A of 1,
The claw portion 34B of the second pawl 30B slides on the teeth 35 of the ratchet wheel 26 to cause the ratchet wheel 26 to slide.
The relative position of the swing axis line Y2 of the second pawl 30B and the claw portion 34B of the second pawl 30B that engages with the teeth 35 of the ratchet wheel 26 is set so as not to rotate.

With this structure, by rotating the handle 3 in the first direction A, the ratchet wheel 2 is rotated.
By rotating 6 in the first direction A and conversely by rotating the handle 3 in the second direction B, the ratchet wheel 2
6 can be rotated in the second direction B.

FIG. 10 is a perspective view showing an example of the above-mentioned return spring, and the return spring 39 shown here is a torsion coil spring (the return spring 39 is not shown in the drawings other than FIG. 10). . When the handle 3 is in the neutral position shown in FIG. 7, the ends 39A and 39B of the return spring 39 are formed on the side edges of the rising portion 23A (not shown in FIGS. 5 and 6) of the handle bracket 23. While being pressed against the notches 40A and 40B, the bent portions at the ends of the respective end portions 39A and 39B have one arm portion 27 of the guide member 27.
It is pressed against the side edges 41A and 41B of A.

When the handle 3 is rotated in the first direction A, the handle bracket 23 rotates in the first direction A together with the handle 3, but the guide member 27 remains stopped, so that one of the return springs 39 is rotated. End 39A
Moves in the first direction A while being engaged with one notch 40A of the handle bracket 23. On the other hand, the other end 39B of the return spring 39 has the guide member 27.
While stopping in pressure contact with the side edge 41B, the notch 40B of the handle bracket 23 separates from the other end 39B of the return spring 39. As a result, elastic energy is accumulated in the return spring 39.

Then, when the handle 3 is released, the elasticity of the return spring 39 causes the handle bracket 23 to receive a force from the first end 39A of the return spring 39, and the handle bracket 23 moves in the second direction together with the handle 3. When the handle 3 is rotated to B and reaches the neutral position shown in FIG. 7, one end portion 39A of the return spring 39 is again provided with one side edge 41 of the guide member 27.
Hit A. In this way, the handle 3 automatically returns to the neutral position and stops there.

When the handle 3 in the neutral position is rotated in the second direction B, the other end 39B of the return spring 39 is moved in the second direction B, contrary to the above.
While moving in the second direction B while being engaged with the notch 40B of the handle bracket 23 that rotates, the one end 39A stops while being pressed against one side edge 41A of the guide member 27. Therefore, if the handle 3 is released in this state, the handle bracket 23 will return to the return spring 39.
The pressure is applied by the other end 39 </ b> B of and the handle 3 automatically returns to the neutral position.

FIG. 11 is a cross-sectional view of the brake mechanism 9 shown in FIGS. 5 and 6. As can be seen from FIGS. 5, 6 and 11, the brake mechanism 9 has a stopper case 42 fixed to the lifter support 8, and the stopper case 42 is formed in a cup shape with one end side opened. ing. The stopper case 42 has an inner wall 42A and an outer wall 42B that are concentric with each other, and the inner wall 42A and the outer wall 42B are integrated via an annular end wall 42C opposite to the open end. The inside of the inner wall 42A is hollow.

A notch is formed in the stopper case 42, and a core 43 having a substantially fan-shaped cross section is rotatably accommodated therein. The shaft 21 passes through the center of the core 43, And the core 43 are fixed to each other, and they can integrally rotate about the above-described rotation axis X.

An annular groove 44 centered on the rotation axis X is formed in the core 43, and the inner side wall 42A of the stopper case 42 is fitted therein, and a small diameter coil spring (torsion spring) is formed inside the inner side wall 42A. ) 45A is arranged. Moreover, a large-diameter coil spring (torsion spring) 45B is arranged between the outer peripheral surface of the core 43 and the inner peripheral surface of the outer wall 42B of the stopper case 42.

Further, the stopper plate 46 is rotatably accommodated in the stopper case 42, and the claw portion 46A thereof is provided.
Are located in the cutout space of the core 43. An annular groove 47 centered on the rotation axis X is also formed in the claw portion 46A of the stopper plate 46, and the inner side wall 42A of the stopper case 42 and the small-diameter coil spring 45A are arranged in the annular groove 47. The shaft 21 is relatively rotatably fitted into the through hole 48 (FIG. 5) of the stopper plate 46, and the above-mentioned pinion 6 is fixed to the stopper plate 46.

One end portion (hook portion) 49A of the large-diameter coil spring 45B is engageable with one circumferential end wall surface 50A of the core 43, and the other end portion (hook portion) 49B of the spring 45B is connected. Holes 51 formed in the stopper plate 46
It is locked to A. Further, one end portion (hook portion) 52A of the small-diameter coil spring 45A can be engaged with the other circumferential end wall surface 50B of the core 43, and the other end portion (hook portion) 52B of the spring 45A has a stopper plate 46. It is locked in the hole 51B formed in.

As can be seen from the above, the shaft 21
Is rotatably supported with respect to the lifter support body 8 via the core 43, the stopper plate 46 and the stopper case 42, and the pinion 6 is also rotatable with respect to the lifter support body 8 via the stopper plate 46 and the stopper case 42. And is concentric with the shaft 21.

When the ratchet wheel 26 and the shaft 21 are rotated in the first direction A by rotating the handle 3 in the first direction A as described above, the core 43 in the stopper case 42 is also changed. Rotate in the same first direction A. As a result, the other circumferential end wall surface 50B of the core 43 is formed.
Pressurizes one end 52A of the small diameter coil spring 45A,
As a result, the diameter of the small-diameter coil spring 45A is reduced, and the small-diameter coil spring 45A and the inner wall 42 of the stopper case 42 are
The pressure contact force with A decreases. As a result, the core 43 can rotate in the first direction A together with the stopper plate 46, and accordingly, the pinion 6 rotates in the first direction A.

By rotating the handle 3 in the second direction B, even when the core 43 rotates in the same second direction, one circumferential end wall surface 50A of the core 43 has a large-diameter coil spring. It engages with one end 49A of 45B and pressurizes it. As a result, the diameter of the large-diameter coil spring 45B is reduced, and the pressure contact force between the coil spring 45B and the outer side wall 42B of the stopper case 42 is weakened, so that the core 43 together with the stopper plate 46 and the pinion 6 moves in the second direction B. Rotate to.

On the other hand, for example, when the seat cushion 1 is at the uppermost position and a large load is applied to the seat cushion 1 due to a seated person sitting on the seat cushion 1 as shown in FIG. A rotational force in the direction in which the rack 11 rotates in the clockwise direction in the figure acts on the rack 11 via the connecting link 20. For this reason,
Rotational force is applied to the pinion 6 and the stopper plate 46 via the rack 11 in a direction in which the pinion 6 and the stopper plate 46 rotate in the counterclockwise direction (second direction B) in FIG. 3. However, at this time, since one end 49B of the large-diameter coil spring 45B is engaged with the hole 51A of the stopper plate 46, the diameter of the large-diameter coil spring 45B is increased, and the coil spring 45 is expanded.
A large frictional force acts between B and the outer wall 45B of the stopper case 42. Therefore, although the pinion 6 may rotate very slightly in the second direction B, it does not rotate largely. As a result, even if a large load is applied to the seat cushion 1, it will not descend.

Further, the pinion 6 and the stopper plate 46
On the other hand, when a rotational force in a direction in which these rotate in the clockwise direction (first direction A) in FIG. 11 is applied,
Since the other end 52B of the small-diameter coil spring 45A is locked in the hole 51B of the stopper plate 46, the small-diameter coil spring 45A has a larger diameter, and the coil spring 45A concerned.
A large frictional force acts between the inner wall 42A of the stopper case 42 and the inner wall 42A. Therefore, although the pinion 6 and the stopper plate 46 may rotate very slightly in the first direction A, they are prevented from rotating largely.

As described above, the brake mechanism 9 includes the shaft 21
Is allowed to be transmitted to the rotating body composed of the pinion 6, but when the rotating force is applied to the rotating body other than the shaft 21, that is, from the seat cushion 1 side, the rotating body rotates. An example of the prohibiting braking means is configured. By providing such braking means,
After adjusting the height of the seat cushion 1, even if an external force is applied to the seat cushion 1, the seat cushion can be prevented from descending or rising.

Then, the brake mechanism 9 of the present embodiment example
In the above, between the inner wall surface of the end wall 42C of the case 42 and the surface of the core 43 that faces the end wall 42C of the case 42, a spacer 100 that contacts both of them is provided.
As a material of the spacer 100, there is a polyether elastomer.

Due to the frictional force generated between the spacer 100 and the core 43, the spacer 100 is moved to the core 43 (shaft 2).
It is a resistance means for suppressing the rotation of 1). The resistance value of the spacer 100 causes the claw portion 34B of the pole 30A or the claw portion 34B of the pole 30B to slide on the teeth 35 of the ratchet wheel 26 when the handle 3 is released and the handle 3 is returned to the neutral position. At this time, the force to rotate the ratchet wheel 26 (shaft 21) (axis return force)
It is set to a greater power.

According to the above configuration, the following effects can be obtained. (1) The brake mechanism 9 is provided with the spacer 100 as a resistance means for suppressing the rotation of the shaft 21, so that when the handle 3 returns to the neutral position, the shaft returning force acting on the shaft 21 is overcome. Even if the handle 3 is returned to the neutral position, there is no play in the rotation direction of the shaft 21. Therefore, the loss of the steering wheel operation amount is reduced.

(2) A desired resistance value can be obtained by changing the material and thickness of the spacer 100 and the area of contact with the inner wall of the stopper case 42 and the core 43. (3) In the seat lifter of the present embodiment, a guide member 27 having an arc-shaped elongated hole 29 centered on the rotation axis X of the handle 3 is slidably fitted in the elongated member 29. And has pole support members 31A and 31B that swingably support the first and second poles 30A and 30B, and the respective end portions 29A and 29B of the elongated hole 29 have pole support members 31A and 31B. It is configured to serve as a stopper for. The elongated hole 29 of the guide member 27 allows the first and second pawls 30A and 30B to be properly guided and revolved around the rotation axis X, and the ends 29A and 29B of the elongated hole 29 can be revolved. Has a function as a stopper for stopping the respective poles 30A, 30B, the first and second poles 30A, 30
Since it is not necessary to separately provide a guide member for guiding B and a stopper for stopping the guide member, it is possible to reduce the number of parts of the seat lifter.

(4) In the seat lifter of the present embodiment, the claw portions 34 of the first and second poles 30A and 30B are included.
A spring 38, which is an example of a biasing means for biasing each of the pawls 30A, 30B toward the teeth 35 of the ratchet wheel 26, is provided so that the teeth A, 34B are securely engaged with the teeth 35 of the ratchet wheel 26. As a result, the ratchet wheel 26 can be correctly rotated by the revolution of the first and second poles 30A and 30B. Moreover, the spring 38 of the illustrated example has the holding portions 38A, 3 for holding the first and second pawls 30A, 30B together.
Since it consists of one leaf spring with 8B, the spring 38
The structure of can be simplified.

The present invention is not limited to the above embodiment. The resistance means may have a configuration as shown in FIGS. In FIG. 12, the core 43 is formed with a projection 103 that comes into contact with the inner wall surface of the end wall 42C of the case 42, and serves as a resistance means. Since only the protrusion 103 is formed on the core 43, the cost can be reduced.

In addition, a protrusion that abuts the core 43 may be formed on the inner wall surface of the end wall 42C of the case 42, or the core 4
3. A protrusion may be formed on the stopper case 42. Figure 1
3, the shaft 21 is rotatably supported in the burring hole 8C of the supporting portion piece 8A fixed to the lifter supporting body 8, and the burring (cylindrical surface) of the burring hole 8C is used.
Is plastically deformed to increase the contact pressure with the shaft 21 to serve as resistance means. A desired resistance value can be obtained depending on the degree of plastic deformation. Further, the desired resistance value can be obtained even if the contact area between the burring and the shaft and the material of the burring and the shaft are changed.

In FIG. 14, the through hole 48 of the stopper plate 46 rotatably supporting the shaft 21 and the shaft 21 are shown.
An O-ring 105 is provided between and to serve as resistance means.
A desired resistance value can be obtained by changing the material and size of the O-ring 105.

Further, in the illustrated example, the first and second pole support members 31A and 31B are provided, and the first and second poles 30A and 30B are swingably supported respectively, but one pole is provided. A support member may be provided, and one pole support member may support both the first and second pawls 30A and 30B swingably.

Various forms of braking means other than the illustrated braking mechanism 9, for example, a braking mechanism having one torsion spring as shown in the conventional example can be adopted.
Furthermore, the present invention is not limited to a seat lifter mechanism that raises and lowers a seat cushion of a seat provided in a passenger compartment of an automobile, but is also applied to a vertical mechanism that raises and lowers only a front portion or a rear portion of the seat cushion, a tilt mechanism that tilts the seat cushion, and the like. it can.

[0074]

As described above, according to the first aspect of the present invention, the ratchet mechanism is provided when the handle is returned to the neutral position by providing the resistance means for applying the resistance force to the rotation of the shaft of the brake mechanism. By sliding the ratchet teeth of the ratchet and the engaging member to overcome the axial return force acting on the shaft, there is no play in the rotational direction of the shaft even when the handle is returned to the neutral position. Therefore, the loss of the steering wheel operation amount is reduced.

According to the second aspect of the present invention, the desired resistance can be obtained by changing the material and thickness of the spacer contacting the inner wall of the stopper case and the core, and the area of contacting the inner wall of the stopper case and the core. You can get the value.

According to the third aspect of the present invention, the resistance means is a protrusion formed on at least one of the stopper case and the core and abutting against the other, thereby reducing the cost. Can be planned.

According to the fourth aspect of the invention, a desired resistance value can be obtained by changing the contact area between the bearing and the shaft, the contact pressure, and the material of the bearing and the shaft.

[Brief description of drawings]

FIG. 1 is a side view of a seat.

FIG. 2 is a diagram showing a state of a transmission unit when a seat cushion is at an intermediate height position.

FIG. 3 is a view showing a state of the transmission means when the seat cushion is at the uppermost position.

FIG. 4 is a view showing a state of the transmission means when the seat cushion is at the lowest position.

FIG. 5 is a cross-sectional view of a handle and a transmission mechanism that transmits rotation of the handle to a pinion.

FIG. 6 is an exploded cross-sectional view showing the elements shown in FIG. 5 separately.

FIG. 7 is a diagram illustrating a positional relationship between a handle and first and second poles.

FIG. 8 is a diagram showing a part of elements of a transmission mechanism.

FIG. 9 is a diagram illustrating an engagement state of pawl claws and ratchet wheel teeth.

FIG. 10 is a perspective view showing a return spring.

FIG. 11 is a cross-sectional view of the brake mechanism.

FIG. 12 is a diagram illustrating another example of resistance means.

FIG. 13 is a diagram illustrating another example of the resistance means.

FIG. 14 is a diagram illustrating another example of resistance means.

FIG. 15 is an exploded perspective view of a conventional brake mechanism.

16 is a cross-sectional view of the brake mechanism of FIG.

[Explanation of symbols]

3 handles 8 Lifter support 21 axis 26 ratchet wheel 29 slot 29A end 29B end 30A first pole 30B 2nd pole 31A Pole support member 31B Pole support member 34A Claw 34B Claw 35 teeth 36 cam 42 Stopper case 45A coil spring (torsion spring) 45B coil spring (torsion spring) 46 Stopper plate 46A claw 100 spacer (resistive means) A first direction B second direction X rotation axis Y1 swing shaft Y2 swing shaft

Claims (4)

[Claims] 1. A torsion spring having hooks at both ends is arranged in the stopper case so as to abut against the inner wall of the stopper case, and a shaft side core having a cutout is rotatable on the inner wall of the torsion spring. A brake mechanism in which a claw portion of a stopper plate integrally formed with the rotating body is inserted into the notched space of the core, and a ratchet and an engaging member that engages ratchet teeth of the ratchet. And a ratchet mechanism for rotating the shaft of the brake mechanism in the one direction by reciprocally moving the handle biased to the neutral position in the one direction from the neutral position. In the above, a resistance means for giving a resistance force to rotation of the shaft of the brake mechanism is provided, and when the handle returns to the neutral position, the ratchet A transmission mechanism, characterized in that a sliding force between a ratchet tooth of the ratchet of the mechanism and the engaging member overcomes an axial returning force acting on the shaft. 2. The transmission mechanism according to claim 1, wherein the resistance means is a spacer that contacts the inner wall of the stopper case and the core. 3. The transmission mechanism according to claim 1, wherein the resistance means is a projection formed on at least one of the stopper case and the core and abutting against the other. 4. The transmission mechanism according to claim 1, wherein the resistance means is provided in a bearing portion that rotatably supports the shaft.