JPH023703A - Brake mechanism - Google Patents

Abstract

PURPOSE:To suppress the chattering of an output member and a core due to vibration by accommodating the core having two cut parts inside two springs installed inside a housing and freely inserting the hook of the output member into the cut parts and engagement-arranging the edge part of the spring with the hook and the cut side wall. CONSTITUTION:The detent 14 of an output member 12 is freely inserted into a space between the first and second cut parts 8A and 8B of a core which is accommodated in turnable ways inside the springs 3 and 5 which are installed in press-attachable ways onto the inner wall of a housing 1. Further, the hook part 3A of the spring 3 is engaged with the engaging groove 14A of the detent 14, and the hook part 3B is arranged on the side wall 8Bb of the cut part 8B, and the hook part 5A of the spring 5 is arranged between the side wall 8Aa of the cut part 8A and the side wall 14C of the detent 14, and the hook part 5B is arranged in the intermediate position between the side wall 8Ab of the cut part 8A and the side wall 14B of the detent 14. Therefore, the chattering of the output member 12 and the core 7 due to vibration, etc. can be suppressed to the min.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a brake mechanism, and particularly to a brake mechanism used in a vehicle seat vertical adjustment device, a wind regiator, and the like.

[Prior Art] In general, such a brake mechanism is a device that transmits rotational force applied from an input side such as a steering wheel to an output side such as a pinion, and raises and lowers a vehicle window glass or seat etc. by operating the handle. It is used to prevent window glass or sheets from falling under their own weight or load.

Therefore, such a brake mechanism is required to provide sufficient braking force to prevent the heavy object from descending and to minimize backlash due to vibrations and the like.

Conventionally, as such a brake mechanism, for example, Japanese Patent Application Laid-Open No. 58
The conventional technique shown in FIG. 1 of Japanese Patent No. 152944 is generally used.

In this brake housing, a torsion spring is arranged in pressure contact with the inner wall of the housing, and a claw part provided integrally with the pinion protects the spring against rotational force from the pinion side. Since the hook part is pushed and the outer diameter of the spring is expanded, the pressing force between the spring and the housing becomes strong, and rotation of the pinion is prevented. On the other hand, in response to a rotational force from the core provided integrally with the handle shaft, the spring receives a force in a direction that reduces the outer diameter, so that the core becomes rotatable. Therefore, the pinion can be rotated via the spring and the pawl. That is, rotation can be transmitted from the handle shaft side, but rotation cannot be transmitted from the pinion side.

In addition, in order to eliminate the drawbacks of the above, the above publication uses two springs, both ends of which are engaged with pawls on the pinion side, and both ends are engaged with the side ends of the core. A possible arrangement is 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 rotational direction of the pinion due to the gap corresponding to the amount of winding of the spring and the gap for absorbing product processing errors, which causes backlash and makes it difficult to obtain a good feeling. There was a problem.

In the latter case, although two springs were used to absorb the above-mentioned play, the braking force for rotation in one direction is provided by one spring, and the braking force for rotation in the other direction is provided by the other spring. Even if you try to obtain the same braking force as before, you will need storage space for two springs, making the device larger and making it impossible to suppress the backlash of the core, that is, the handle. There was a problem.

The purpose of the present invention is to solve the problems of the conventional brake mechanism, to provide a brake mechanism that can obtain the large braking force required for such a mechanism, minimize backlash, and reduce costs. It is about providing.

[Means for Solving the Problems 1] In order to achieve the above object, the present invention provides a first and a second brake housing which are arranged in a brake housing so as to be able to be press-contacted with the inner wall of the housing.
A core provided with a first notch and a second notch larger than the first notch is rotatably housed inside the first and second springs;
An output member having a pawl that is loosely inserted into the space of both notches of the core is rotatably provided, one end of the first spring is locked to the pawl of the output member, and the other end is attached to the second notch of the core. The second spring is arranged so as to be able to come into contact with the side wall, and both ends of the second spring are arranged between the first notch side wall and the claw.

[Function] According to the present invention, when the core is rotated as an input, one end of the second spring immediately comes into contact with the side wall of the first notch of the core and also with the claw. Since the two springs are in contact with each other and one end of the first spring is locked with this pawl, the diameters of the first and second springs are reduced and the output member is rotatable. Also, for rotation in the opposite direction, the first
and both ends of the second spring are the respective second ends of the core.
Since the springs are in direct contact with the side walls of the first notch and the diameters of both springs are reduced, the output member can be rotated via the claws. Furthermore, since both springs immediately come into contact with both notch side walls of the core at this time, play on the input side can be suppressed to an extremely small level.

Next, in response to an external force from the output member, when the output member rotates in one direction, the other end of the second spring is pushed by a claw, and the diameter of the second spring expands to obtain a braking force. One end of the first spring is locked to a pawl, and the first
The spring rotates easily and its movement is transmitted to the other end.
Shakiness is reliably prevented when the seat is incorporated into a seat vertical adjustment mechanism, etc.

In addition, when rotating in the opposite direction, the ends of both the first spring and the second spring are pushed by the claws, so that the diameters of both expand, and twice the braking force is obtained.

In the above case, by providing the second notch, the first
Both of the second spring and the second spring can be springs with the same distance between their respective ends, that is, springs with the same shape, and are arranged with the distance between each spring end and the side wall of the pawl and notch small. This allows the backlash to be reduced.

[Example 1 Embodiments of the present invention will be described below with reference to the accompanying drawings.

An embodiment of the present invention is shown in FIGS. 1 and 2. FIG.

In the figure, 1 is a brake housing having a bearing boss 1^ in the center, and inside this brake housing 1,
A coil-shaped first spring 3 and a second spring 5 are mounted so as to be able to come into pressure contact with the inner wall 1B. Both springs 3.5 each have an inwardly bent hook portion 3^, 3B and 5A, 5B at its end.

7 is a first notch a^ (having opposing side walls 8^a and 8^b) on one side of the cylindrical member, and a second notch 8B which is large and shares one side wall with this. (having side walls 88a and 8Bb facing each other), and supports an output member including a handle shaft 9 having serrations on the negative side to which a handle (not shown) is engaged, and a binion to be described later on the other side. A supporting shaft lO is integrally formed.

Reference numeral 12 designates an output member, in which a pinion 13 supported on the support shaft IO and a pawl 14 (having side walls 14B and 14C) are integrally formed, and the pawl 14 has an engagement groove 14^ in its center. There is.

Thus, the core 7 is rotatably supported with the handle shaft 9 by the bearing boss l^ of the brake housing 1, and is housed inside the first spring 3 and the second spring 5.

The hook portion 3^ at one end of the first spring 3 is engaged with the engagement groove 14^ of the pawl 14 that is loosely inserted into the spaces of the first!5 and second notches 8A and aB of the core 7. , the hook portion 3B at the other end is arranged near the side wall 8Bb of the second notch 8B (see FIG. 3).

The hook part 5^ at one end of the second spring 5 is arranged between the side wall BAa of the first notch 8^ and the side wall 14c of the claw 14, and the hook part 5^ is arranged between the side wall BAa of the first notch 8^ and the side wall 14c of the claw 14. While in contact with both, the hook portion 5B at the other end is located midway between the side wall 8^b of the first notch 8^ and the side wall 14B of the claw 14 (see Fig. 3). ).

The end of the support shaft lO is supported by a cover 15 fixed to the brake housing l (see FIG. 2).

Next, FIG. 4 shows how the brake mechanism of this embodiment having the above-mentioned structure is incorporated into a seat vertical adjustment mechanism.

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

A shaft 41 is rotatably supported on the seat frame 40, and a sector gear 42 is attached to the shaft 41.
is permanently installed. The sector gear 42 is biased clockwise in the drawing by a spring 41 wound around the shaft 41.

The upper rail 30 has first and second support brackets 4.
3 and 44 are fixedly installed, the tip of the first support bracket 43 is rotatably fixed to the sector gear 42 with a pin 43^, and the tip of the second support bracket 44 is fixed to the frame 4.
0 by a pin 44A to an intermediate bracket 45 which is rotatably secured to the intermediate bracket 45 by a pin 45^.

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

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

H is a handle inserted into the serrations of the handle shaft 9.

When the brake mechanism B having the above-described structure is incorporated into the seat vertical adjustment mechanism, the sector gear 42 is urged to rotate clockwise by the action of the spring 41A, and as a result, the sector gear 42 is urged to rotate clockwise. Rotate.

Then, a counterclockwise rotational force is applied from the output member 12, and the claw 14 rotates counterclockwise together with the first spring 3 to which the hook portion 3^ is engaged, and the side wall 14B of the claw 14 rotates counterclockwise together with the first spring 3 to which the hook portion 3^ is engaged. 5 comes into contact with the hook portion 5B of No. 5. Further, the hook portion 3B of the first spring 3 is close to the side wall 8Bb of the second notch 8B.

Then, since the side wall 14B of the claw 14 comes into contact with the hook portion 5B, the rotation of the output member 12 is prevented by the braking force caused by the diameter expansion action of the second spring 5, and as shown in FIG.
) is set and maintained in the state shown in ().

In this state, the hook portion 3B of the first spring 3 is close to or in contact with the side wall 8Bb of the second notch 8B, and the hook portion 5A of the second spring 5 is in contact with the side wall 8Bb of the second notch 8B. Since it is in contact with the side wall 8^a, the looseness of the core 7, that is, the handle H can be suppressed as much as possible.

In this state, when the handle H side, that is, the core 7 side is rotated clockwise, the diameter of the first spring is immediately reduced by the side wall 8Bb with which the hook portion 3B is in proximity or in contact, and the second spring 5 is After the hook part 5B moves a predetermined distance 1, the diameter of the hook part 5B is reduced and the claw 14
The output member 12 is also rotated clockwise via the rotor, and the sector gear 42 is rotated counterclockwise to lower the seat.

Further, when the handle H is rotated counterclockwise, the second spring 5 moves to the side wall 8A with its hook portion 5^ in contact.
The diameter of the first spring 3 is immediately reduced by a, and the hook portion 5^ of the second spring 5 moves a predetermined distance 1, and then the hook 1 of the first spring 3
The diameter of the claw 1 is reduced by contacting the side wall 14G of the claw 1.
4, the output member 12 can be rotated counterclockwise to raise the seat.

Next, when a clockwise rotational force is applied from the output member 12 side in the state shown in FIG. 3(a), that is, when a load is applied on the seat, first the hook portion 3^ with the claw 14 in the locked state The diameter of the first spring 3 is expanded without causing any play, and a braking force is immediately obtained. With further rotation, the side wall 14C of the claw 14 comes into contact with the hook portion 5A, so the braking force by the second spring 5 is increased. (Figure 3 (
(see b)), when a rotational force is applied in the counterclockwise direction due to vibrations of the vehicle, the side wall 14B of the pawl 14 presses the hook portion 5B of the second spring 5 that is in contact with the hook portion 5B of the second spring 5. 2 spring 5 is expanded in diameter, and braking force is immediately obtained without causing backlash.

Therefore, braking force can be obtained without causing play in response to input from the output member 12 in both directions, and braking force from the two springs can be obtained in response to input in the clockwise direction. .

[Effects of the Invention] As is clear from the above description, according to the present invention, a large braking force can be obtained in a direction where a large braking force is required, and play in the output member and the core, that is, the handle due to vibration etc. can be reduced. can be reliably minimized.

Furthermore, since two springs having the same shape can be used, there is no need to prepare them separately, and costs can be reduced.

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view of the constituent parts of an embodiment of the present invention, Fig. 2 is a partially sectional side view of the assembled state, and Fig. 3 is the same as that shown in Fig. 2 for explaining its operation. FIG. 4 is a perspective view showing how the brake mechanism according to the present invention is incorporated into a seat vertical adjustment device. DESCRIPTION OF SYMBOLS 1... Brake housing, 3... First spring, 5... Second spring, 7... Core, 8^... First notch, 8B... Second notch, 9... Handle shaft, 12... Output member, 13... Pinion, 14... Pawl, 14^... Engagement groove.

Claims (1)

[Claims] 1) A first and second spring is mounted in the brake housing so that it can be pressed into contact with the inner wall of the housing, and a core is provided with a first notch and a second notch larger than the first notch. An output member is rotatably housed inside the first and second springs and has a claw that is loosely inserted into the spaces of both notches of the core, and 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 against the second notch side wall of the core, and both ends of the second spring are arranged between the first notch side wall and the claw. A brake mechanism characterized by being arranged in.