JPH0678774B2 - Brake mechanism - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a brake mechanism, and more particularly to a brake mechanism used in an up / down adjusting device for a vehicle seat, a window regulator, and the like.

[Prior Art] Generally, such a brake mechanism is a device for transmitting a rotational force applied from an input side of a steering wheel or the like to an output side of a pinion or the like, and raising or lowering a window glass or a seat of a vehicle by operating the steering wheel. It is used to prevent the window glass or sheet from falling due to its own weight or load.

Therefore, in such a brake mechanism, it is required that the braking force is sufficient to prevent the descent of heavy objects and that the backlash due to vibration or the like is minimized.

Conventionally, as such a brake mechanism, for example, JP-A-58-1
What is described as a prior art in FIG. 1 of 52944 is generally used.

In the brake housing, a torsion spring is arranged so as to come into pressure contact with the inner wall of the housing, and a claw portion provided integrally with the pinion is a spring against the rotational force from the pinion side. Since the hook portion is pushed to widen the outer diameter of the spring, the pressure contact force between the spring and the housing becomes strong, and the rotation of the pinion is prevented. On the other hand, with respect to the rotational force from the core side provided integrally with the handle shaft, the spring receives a force in the direction of reducing the outer diameter, so that the core can rotate. Therefore, the pinion can be rotated via the spring and the claw portion. That is, the rotation can be transmitted from the handle shaft side, but the rotation cannot be transmitted from the pinion side.

Further, in order to solve the drawbacks of the above, in the above publication, two springs are used, one end of each of these springs is locked to a claw on the pinion side, and the other ends thereof are engaged with side end portions of the core. The possible arrangements are shown.

[Problems to be Solved by the Invention] However, in the former of the above-mentioned conventional mechanisms,
As pointed out in the publication, there is a large amount of play in the pinion rotation direction due to the gap corresponding to the amount of spring entrainment and the gap for absorbing product processing error, and it is said that play cannot be obtained due to backlash. There was a problem.

In the latter case, two springs are used to absorb the backlash, but the braking force for rotation in one direction is for one spring, and the braking force for rotation in the other direction is for the other spring. Even if you try to obtain a braking force equivalent to the conventional one, you need a storage space for two springs, the size of the device becomes large, and you cannot press the backlash of the core or handle. There was a problem.

An object of the present invention is to solve the problems of the conventional brake mechanism, to obtain a large braking force required for such a mechanism, and to minimize play, particularly play on the pinion side in addition to the core. It is to provide a brake mechanism that can

[Means for Solving the Problems] In order to achieve the above object, the present invention includes a first and a second brake housing, which are press-contactable with an inner wall of the housing.
A spring is mounted, and a core provided with a notch is rotatably housed inside the first and second springs, and an output member having a claw that is loosely inserted in the space of the notch of the core is rotatable. The first spring is locked to the claw of the output member, and the other end of the first spring is abutted against the side wall of the core cutout, and both ends of the second spring are arranged between the side wall of the cutout and the claw. In the state where one end of the second spring is sandwiched between one end side of the core cutout side wall and one end side of the claw, the other ends of the first and second springs and the core cutout side wall are The distance from the end side is set to be equal to or more than the distance between the other ends of the first and second springs and the other end of the claw.

[Operation] According to the present invention, when the core is rotated as an input, one end of the second spring immediately contacts the side wall on the one end side of the core notch and also on one end side of the claw with respect to the one-way rotation. Since the first spring and the second spring are in contact with each other and one end of the first spring is locked by the claw, the diameters of the first and second springs are reduced and the output member is rotatable. Also, in the opposite direction rotation, the other ends of the first and second springs are brought into immediate contact with the side wall on the other end side of the core cutout, and the two springs are reduced in diameter to prevent the rotation of the output member. It becomes possible.
In addition, at this time, since both springs immediately contact the core cutout side wall, the play on the input side can be suppressed to be extremely small.

Next, with respect to the external force from the output member, the one end of the second spring pushes the other end of the second spring by the one end rotation of the output member, and the second spring expands to increase the braking force. can get.

In the reverse rotation, one end of the claw comes into contact with one end of the second spring and one end of the first spring is locked by the claw, so that the first and second springs respectively expand in diameter. Double the braking force.

In this case, when the output member is rotated toward the other end side of the first and second springs due to the play of the output member due to the gap with the core cutout, the core cutout is sandwiched by sandwiching the other ends of these first and second springs. The other end of the claw of the output member contacts the side wall on the other end side of the notch, and further rotation of the output member is prevented. In addition, the rotation of the output member in the opposite direction is prevented by at least the braking force generated with the expansion of the diameter of the first spring. That is, in this state, the backlash of the output member is eliminated.

[Embodiment] An embodiment of the present invention will be described below with reference to the accompanying drawings.

1 and 2 show an embodiment of the present invention.

In the figure, reference numeral 1 denotes a brake housing having a bearing boss 1A in the center thereof, and a coil-shaped first spring 3 and a second spring 5 are mounted in the brake housing 1 so as to be capable of press-contacting an inner wall 1B thereof. . Each of these springs 3 and 5 has hook portions 3A and 3B and 5A and 5B formed by bending the inside thereof at the ends thereof.

7 is a notch on the negative side of the disk-shaped member 8 (side walls 8A and 8B facing each other)
Handle shaft 9 having a serration with which a handle (not shown) is engaged on the negative side,
On the other side, a support shaft 10 for supporting an output member including a pinion described later is integrally formed.

Reference numeral 12 is an output member, which is a pinion 13 supported by the support shaft 10.
And the claw 14 (having side walls 14B and 14C) are integrally formed, and the claw 1
4 has an engaging groove 14A at its center.

The core 7 is rotatably supported on the handle shaft 9 by the bearing boss 1A of the brake housing 1 and is housed inside the first spring 3 and the second spring 5.

Then, the hook portion 3A at one end of the first spring 3 is locked in the engaging groove 14A of the claw 14 which is loosely inserted into the space of the notch 8 of the core 7, and the hook portion 3B at the other end of the notch 8 is formed. It abuts against the side wall 8B and is locked (see FIGS. 3 (b) and 3 (c)).

The hook portion 5A at one end of the second spring 5 is locked while abutting on both the side wall 8A of the cutout 8 and the side wall 14B of the claw 14, and the hook portion 5B at the other end is hooked to the side wall 8B of the cutout 8 and the claw. 14 side walls
It is located between 14C (see FIG. 3 (a)).

The end of the bearing shaft 10 is supported by a cover 15 fixed to the brake housing 1 (see FIG. 2).

In this example, the hook portions 3B and 5B at the other ends of the first spring 3 and the second spring 5 are arranged so as to overlap with each other at the same position in the middle between the side wall 8B of the notch 8 and the side wall 14C of the claw 14. Moreover, the side walls 8B and 14C on both sides of the hook portions 3B and 5B
And the distances Al and Bl are arranged so that Al ≧ Bl) (see FIG. 3 (a)).

By doing so, for example, when a clockwise rotational force is applied from the output member 12 side, the claw 14 rotates clockwise Bl together with the first spring 3 to which the hook portion 3B is locked, and the side wall 14C thereof. It abuts on the hook portion 5B of the second spring 5.
In addition, the hook portion 3B of the first spring 3 is the side wall 8B of the core 7.
Close to.

Then, the rotation of the output member 12 is blocked by the braking force due to the expanding action of the second spring 5 as in the previous embodiment. However, when the external force from the output member 12 is removed, as shown in FIG. 3 (b). It is set and held in the state shown. This means that when the brake mechanism is operated once after being assembled in the state of FIG. 3 (a), the state is set to the state of FIG. 3 (b). In this state, since the hook portion 3B of the first spring 3 is close to the side wall 8B of the core 7, it is possible to suppress the play of the core 7, that is, the handle as much as possible.

In this state, when the core 7 is rotated counterclockwise from the handle side, the diameters of the first and second springs 3 and 5 are reduced, and the output member 12 is rotated via the claw 14 (see FIG. )reference). The same applies when the core 7 rotates clockwise.

Next, when a rotational force is applied counterclockwise from the output member 12 side in the state of FIG. 3 (b), first the claw 14 presses the hook portion 3A in the locked state to expand the diameter of the first spring 3. Let
The braking force is immediately obtained, and the braking force by the second spring 5 is also obtained by further rotation. Further, when the rotational force is applied in the clockwise direction, the side wall 14C of the claw 14 presses the hook portion 5B of the second spring 5 in the contact state to expand the diameter of the second spring 5 and immediately obtain the braking force. .

Therefore, the braking force can be obtained without rattling against the input from the output member 12 side, and the braking force by the two springs can be obtained for the counterclockwise input.

Next, FIG. 4 shows an example in which the brake mechanism of the present embodiment having the above-mentioned configuration is applied to a seat vertical adjustment mechanism.

In the figure, 20 is a lower rail fixed to the floor surface of the vehicle, 30 is an upper rail slidably provided on the lower rail 20, and 40 is a seat frame vertically adjustable with respect to the upper rail 30. Is.

A shaft 41 is rotatably supported by the seat frame 40, and a sector gear 42 is fixed to the shaft 41. The sector gear 42 is a spring 41 wound around a shaft 41.
It is biased counterclockwise in the figure by A.

First and second support brackets 43 and 44 are fixedly mounted on the upper rail 30, and the tip of the first support bracket 43 is rotatably fixed to the sector gear 42 by a pin 43A. The tip is fixed to the intermediate bracket 45, which is rotatably fixed to the frame 40 by a pin 45A, by a pin 44A.

The sector gear 42 and the intermediate bracket 45 are connected by the arm 46 via the pins 42A and 45B, respectively.

In the brake mechanism B, the brake housing 1 is fixed to the seat frame 40, and the pinion 13 meshes with the sector gear 42.

H is a handle fitted into the serration portion of the handle shaft 9.

Then, when the handle H is rotated clockwise, the pinion 13 also rotates clockwise as described above, and the sector gear 42 rotates counterclockwise. Then, the intermediate bracket 45 is also rotated counterclockwise around the pin 45A via the arm 46,
Raise the seat frame 40.

By stopping the drive from the handle H in this state, the seat load is applied and the sector gear 42 rotates clockwise, that is, even if the pinion 13 tries to rotate counterclockwise, as described above, the pinion 13 rotates counterclockwise. The first and second springs 3 and 5 do not rattle against movement.
The braking force is applied to prevent its rotation.

On the contrary, when lowering the seat frame 40, the handle H may be rotated counterclockwise. Since the handle H coincides with the load direction at this time, the force for rotating the pinion 13 clockwise does not act. Instead, the pinion 13 is immediately held at the position where the rotation of the handle H is stopped.

[Effects of the Invention] As is clear from the above description, according to the present invention, a large braking force can be obtained in the direction in which a large braking force is required, and the backlash of the output member and the core, that is, the handle due to vibration or the like. Can be minimized.

[Brief description of drawings]

FIG. 1 is an exploded perspective view showing components of one embodiment of the present invention, FIG. 2 is a partial cross-sectional side view of the assembled state, and FIG. 3 is a plan view for explaining the operation thereof. FIG. 4 is a perspective view showing a state in which the brake mechanism according to the present invention is applied to a seat up-down adjusting device. 1 ... Brake housing, 3 ... 1st spring, 5 ... 2nd spring, 7 ... Core, 8 ... Notch, 9 ... Handle shaft, 12 ... Output member, 13 ... Pinion, 14 ... Claw, 14A ... Engagement groove.

Claims (1)

[Claims] 1. A first and a second spring are mounted in a brake housing so as to be capable of being pressed against an inner wall of the housing,
A core provided with a notch is rotatably housed inside the first and second springs, and an output member having a claw that is loosely inserted in a space of the notch of the core is rotatably provided. One end of the first spring is locked to the claw of the output member, and the other end is arranged so as to be able to abut the core cutout side wall, and both ends of the second spring are arranged between the cutout side wall and the claw. However, in a state where one end of the second spring is sandwiched between one end side of the core cutout side wall and one end side of the claw, the other ends of the first and second springs and the core cutout side wall are A brake mechanism characterized in that the distance between the other end side and the other end side of the first and second springs and the other end side of the claw is set to be equal to or more than the distance.