JPH0735831B2 - 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] In general, such a brake mechanism is a device for transmitting a rotational force applied from an input side of a handle or the like, which is an operating means, to an output side of a pinion or the like, and raising and lowering a window glass of a vehicle, a seat, or the like. It is used to prevent the window glass or sheet lifted by operation from falling by 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 rattling at the time of operating the steering wheel is minimized.

Conventionally, as such a brake mechanism, for example, Japanese Patent Laid-Open No. 58-
What is described as a prior art in FIG. 1 of Japanese Patent No. 152944 is generally used.

In this structure, a torsion spring is arranged in the housing so as to come into pressure contact with the inner wall of the housing, and the claw portion provided integrally with the pinion is a hook of the spring against the rotational force from the pinion side. Since the outer diameter of the spring is expanded by pushing the portion, 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.

However, as pointed out in the publication, this product has a play in the operation of the core due to the gap corresponding to the winding amount of the spring and the gap for absorbing the product processing error,
There is a drawback in that a good feeling cannot be obtained because the backlash is generated when the handle is operated.

In order to eliminate such a defect, for example, the actual development Sho 61-16
The technique described in Japanese Patent No. 3879 has been proposed.

This is because the claws (projections) of the output member are arranged at intervals in the cutout portion of the core, and both end portions of the coil spring are arranged along the inner peripheral wall of the housing so as to be able to contact both end surfaces of the cutout portion. Has been done.

With another U-shaped spring, one end of which is supported by the core and the other end of which is locked to one end of the coil spring, the one end surface of the notch of the core always contacts the other end of the coil spring. It is configured to be touched.

[Problems to be Solved by the Invention] However, in such a conventional one, one end is supported by the core and the other end is a U-shaped spring locked to one end of the coil spring. Since the spring is always biased, it acts as a biasing force in the direction of reducing the diameter of the coil spring.

Therefore, although it contributes to the elimination of backlash when operating the steering wheel, there is a problem that the original braking force is reduced.

An object of the present invention is to solve the problems of the conventional brake mechanism, and to provide a brake mechanism that can obtain a large braking force required for such a mechanism and can minimize the backlash.

[Means for Solving the Problems] In order to achieve the above object, the first aspect of the present invention is to mount at least one brake spring in a housing so that the brake spring can be pressed against an inner wall of the housing, and a notch is provided. A core member that is rotated by the operating means is rotatably housed inside the brake spring, and an output member having a claw that is loosely inserted in the notched space of the core member is rotatably provided.
One end of at least one brake spring is disposed so as to be able to abut on the cutout side wall of the core member, and further, one end is locked to the core member and is disposed between the pawl and one end of the brake spring. An end is locked to one end of at least one brake spring, and a bias spring is provided to urge the side wall of the cutout of the core member in the direction of abutting against one end of the at least one brake spring. And

According to a second aspect of the present invention, the first and second brake springs are mounted in the housing so as to be capable of being pressed against the inner wall of the housing, and the core member rotated by the operating means is used as the first and second brakes. An output member that is rotatably housed inside the spring and that has a claw portion that is loosely inserted in the notched space of the core member is rotatably provided, and one end of each of the first and second brake springs is output. The claw portions of the member are arranged to be engageable with each other, and the other end of each is arranged to be able to abut on the notched side wall of the core member, and further, both ends are engaged with the output member to separate the core member and the output member. A bias spring for biasing the other ends of the first and second brake springs and the notched side wall of the core member in a direction in which the gaps are substantially equal to each other is provided.

[Operation] According to the first aspect of the present invention, when the core member is rotated in one direction by the operating means, the biasing force of the bias spring causes at least one brake spring on one side wall of the notch of the core member. Since one end of the core member is abutted, the one-way rotation of the core member is immediately transmitted as a force for reducing the diameter of at least one brake spring.

Further, when the core member is rotated in the other direction, the bias spring is rotated while bending the bias member against the biasing force to the core member, and thereafter, the bias spring is brought into contact with the other end of at least one brake spring and To reduce the diameter.

Therefore, in any case, the core member rotates while receiving the urging force of the brake spring or the bias spring, so that there is no backlash.
Moreover, since the bias spring constantly applies a biasing force to at least one brake spring in the radial direction, the braking force does not decrease.

Next, according to the second aspect of the present invention, when the core member is rotated in one direction by the operating means, the core member is rotated while being bent against the biasing force of the bias spring, Then, the first brake spring is brought into contact with the other end of the first brake spring to reduce the diameter of the first brake spring.

Also, when the core member is rotated in the other direction, the core member is rotated while bending the same against the biasing force of the bias spring, and then contacts the other end of the second brake spring. The diameter of this second brake spring is reduced.

Therefore, in any case, since the core member rotates while receiving the biasing force of the bias spring, there is no backlash.

Moreover, since no force for reducing the diameter of the first and second brake springs acts on the first and second brake springs in a stationary state, the braking force does not decrease.

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

FIGS. 1 and 2 show a first embodiment of the present invention.
An example of is shown.

In the figure, reference numeral 1 is a housing having a bearing boss 1A at its center, and a coil-shaped first brake spring 3 and a second brake spring 3 and a second brake spring 3 are provided in the housing 1 so as to be capable of pressure contact with the inner wall 1B.
The brake spring 5 of is attached. Both of these brake springs 3 and 5 have hook portions 3A, 3B and 5a, 5B formed by bending the inside thereof at their ends.

Reference numeral 7 denotes a bias spring which is attached to the outer peripheral portion of the bearing boss 1A and has hook portions 7A and 7B formed by bending the end portions thereof.

8 is a first notch on one side of the cylindrical member 8A (the facing side wall)
8Aa, 8Ab) and a second notch 8B (having side walls 8Ba, 8Bb facing each other) which shares one side wall with this and is formed large, and a hook 7B of the bias spring 7. A core member provided with a stop groove 8C, a handle shaft 9 having serrations for engaging a handle (not shown) on one side, and a support shaft 10 for supporting an output member including a pinion described later on the other side are integrally formed. Is formed in.

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 member 8 is rotatably supported on the handle shaft 9 by the bearing boss 1A of the housing 1 and is housed inside the first brake spring 3 and the second brake spring 5.

Then, the hook portion at one end of the second brake spring 5
5A is locked in the engaging groove 14A of the claw 14 loosely inserted in the space of the first and second notches 8A and 8B of the core 8, and the hook portion 5B at the other end is the side wall of the second notch 8B. It is located near 8Bb.

The hook portion 3A at one end of the first brake spring 3 is arranged between the side wall 8Aa of the first cutout 8A and the side wall 14B of the claw 14 so that the hook portion 3A abuts the side wall 8Aa. 7
The hook portion 7A of the bias spring 7 in which B is locked in the locking groove 8C of the core member 8 is locked. The hook portion 3B at the other end of the first brake spring 3 is arranged between the side wall 8Ab of the first cutout 8A and the side wall 14C of the pawl 14, and the side wall 14C of the pawl 14 is provided.
It is in contact with C (see Fig. 2).

The brake mechanism of this embodiment having the above-described configuration is incorporated in a seat up-down adjusting mechanism, a window regulator, or the like.

Now, taking as an example a case where the brake mechanism having the above-mentioned configuration is incorporated in the seat vertical adjustment mechanism, the pinion 13 of the output member 12 is actuated by the action of a spring (not shown) that urges the seat upward. The sector gear (not shown) that meshes with is urged to rotate clockwise, and as a result,
Rotate the pinion 13 counterclockwise.

Then, the counterclockwise rotational force is applied from the output member 12,
The claw 14 rotates counterclockwise together with the second brake spring 5 to which the hook portion 5A is locked, and the side wall 14C thereof comes into contact with the hook portion 3B of the first brake spring 3. The action of the bias spring 7 in which the hook portion 7B at one end is locked in the locking groove 8C of the core member 8 and the hook portion 7A at the other end is locked in the hook portion 3A at one end of the first brake spring 3 The core member 8 is urged in the counterclockwise direction by the
The side wall 8Aa of the notch 8A is in contact with the hook 3A at one end of the first brake spring 3.

Further, the hook portion 5B of the second brake spring 5 is in a state of being close to the side wall 8Bb of the second cutout 8B.

Then, since the side wall 14C of the claw 14 contacts the hook portion 3B, the rotation of the output member 12 is blocked by the braking force due to the expanding action of the first brake spring 3, and the state shown in FIG. 2 is maintained. To be done.

In this state, the hook portion of the first brake spring 3
Since the core member 8 is biased by the bias spring 7 so that the side wall 8Aa of the first cutout 8A contacts the 3A, the rattling of the core member 8, that is, the handle is suppressed.

When the handle side, that is, the core member 8 side is rotated counterclockwise in such a state, the first brake spring 3 is immediately reduced in diameter by the side wall 8Aa with which the hook portion 3A is in contact, and the second brake spring 5 is After the hook portion 3A of the first brake spring 3 moves a predetermined distance, the side wall of the pawl 14 is moved.
The diameter of the output member 12 is reduced by coming into contact with 14B, and the output member 12 is rotated counterclockwise through the claws 14, so that the seat can be raised without rattling the rotation operation of the handle.

When the handle side, that is, the core member 8 side is rotated in the clockwise direction, the core member 8 rotates against the biasing force of the bias spring 7, and the side wall 8Bb of the core member 8 moves for a predetermined distance, and then the second brake in the proximity state. The second brake spring 5 is contracted by abutting on the hook portion 5B of the spring. Also, the hook portion 3B of the first brake spring 3 is reduced in diameter by the side wall 8Ab contacting after moving a predetermined distance, and the output member 12 is also rotated clockwise through the pawl 14, which is the same as when it is raised. As you can see, the seat is lowered without rattling the rotation of the handle.

Next, in the state shown in FIG. 2, when a rotational force is applied from the output member 12 side in the clockwise direction, that is, when a load is applied on the sheet, first, the claw 14 presses the hook portion 5A in the locked state and rattles. The diameter of the second brake spring 5 is expanded without causing the brake force, the braking force is immediately obtained, and the claw 14 is further rotated.
Since the side wall 14B of the first abutment portion abuts on the hook portion 3A, the braking force by the first brake spring 3 is also obtained. Further, when a rotational force is applied in the counterclockwise direction due to vibration of the vehicle or the like, the side wall 14C of the claw 14 presses the hook portion 3B of the first brake spring 3 that is in contact with the first brake spring. The diameter of 3 is expanded, and the braking force is immediately obtained without backlash.

Therefore, it is possible to obtain a braking force for the inputs from the output member 12 side in both directions without backlash, and to obtain the braking force by the two springs for the input in the clockwise direction, that is, the load direction. it can.

Next, the third embodiment of the second aspect of the first aspect of the present invention will be described.
Shown in Figures and FIG.

The present embodiment is different from the previous embodiment in that the end of the bias spring 7 is locked to the locking groove 8C of the core member 8 and the hook 3A at one end of the first brake spring 3 in the previous embodiment. On the other hand, in the present embodiment, the end portion of the bias spring 7 is connected to the locking groove 8D of the core member 8 and the second brake spring 5.
It is locked to the hook portion 5B at one end of the. Therefore, the locking groove 8D is provided at a position different from the locking groove 8C of the previous embodiment.

Since the other structure is the same as that of the previous embodiment, the same parts are designated by the same reference numerals to avoid redundant description.

An example will be described in which the brake mechanism according to the present embodiment is incorporated in the seat vertical adjustment mechanism as in the previous embodiment.

First, in the assembled state, a force for rotating the pinion 13, that is, the claw 14 in the counterclockwise direction is applied, and the claw 14 rotates in the counterclockwise direction together with the second brake spring 5 to which the hook portion 5A is locked. , Its side wall 14C abuts on the hook portion 3B of the first brake spring 3.

Further, the hook portion 7B at one end is locked in the locking groove 8D of the core member 8, and the hook portion 7A at the other end is locked by the second brake spring 5.
Bias spring 7 locked to hook 5B at one end of
The core member 8 is urged clockwise by the action of
The side wall 8Bb of the notch 8B is in contact with the hook portion 5B at one end of the second brake spring 5.

Further, the hook portion 3A of the first brake spring 3 is in a state of being close to the side wall 8Aa of the first cutout 8A.

Then, since the side wall 14C of the pawl 14 contacts the hook portion 3B, the rotation of the output member 12 is blocked by the braking force due to the expanding action of the first brake spring 3, and the state shown in FIG. 4 is maintained. To be done.

In this state, the hook portion of the second brake spring 5
Since the core member 8 is biased by the bias spring 7 so that the side wall 8Bb of the second cutout 8B comes into contact with 5B, the rattling of the core member 8, that is, the handle is suppressed.

In this state, when the handle side, that is, the core member 8 side is rotated counterclockwise, the core member 8 rotates against the biasing force of the bias spring 7, and the side wall 8Aa of the core member 8 moves for a predetermined distance and is in the proximity state. The first brake spring 3 is contracted by coming into contact with the hook portion 3A of the brake spring. Further, the second brake spring 5 is reduced in diameter by the hook portion 3A of the first brake spring 3 coming into contact with the side wall 14B of the moving claw 14 for a predetermined distance, and the output member 12 is counterclockwise via the claw 14. The seat can be lifted without any rattling when the handle is rotated.

When the handle or core member 8 is rotated clockwise, the diameter of the second brake spring 5 is immediately reduced by the side wall 8Bb with which the hook portion 5B is in contact, and the first brake spring 3 is in the proximity state. After the side wall 8Ab moves by a predetermined distance, it comes into contact with the hook portion 3B to be reduced in diameter, and the output member 12 also rotates clockwise through the claw 14.
Then, as in the case of raising, the seat can be lowered without rattling the rotation operation of the handle.

When a rotational force is applied from the output member 12 side in the state of FIG. 4, that is, when a load is applied from the seat side, the same operation as that described in the previous embodiment with reference to FIG. 2 is performed. Avoid duplicate explanations.

Next, a fifth embodiment of the third aspect of the present invention is described.
Shown in Figures and 6.

The present embodiment is a modification of the first embodiment described above, and the modification is that the position where the bias spring 7 is provided is different.

That is, although the bias spring 7 is arranged on the lower surface side of the core member 8 in the first embodiment, it is arranged on the upper surface side of the core member 8 in the present embodiment.

Therefore, a recess 8E is formed on the upper surface side of the core member 8, and a locking groove 8F is formed in the side wall 8Ab of the first cutout 8A.

Then, hook portion 7B of bias spring 7 is engaged with locking groove 8F.
Then, the hook portion 7A is locked to the hook portion 3A of the first brake spring 3.

Since other configurations are the same as those of the first embodiment, the same parts are designated by the same reference numerals.

Since the rattling prevention action of the handle or core member 8 and the braking action on the output member 12 of this embodiment are the same as those of the first embodiment, the description thereof will be omitted. However, in this embodiment, since the bias spring 7 is assembled on the upper surface side of the core member 8, the assembling work is easy.

Next, a seventh embodiment of the first embodiment of the second aspect of the present invention will be described.
Shown in FIGS.

In the figure, reference numeral 1 is a housing having a bearing boss 1A at its center, and a coil-shaped first brake spring 3 and a second brake spring 3 and a second brake spring 3 are provided in the housing 1 so as to be capable of pressure contact with the inner wall 1B.
The brake spring 5 of is attached. Each of these brake springs 3 and 5 has hook portions 3A, 3B and 5A, 5B formed by bending inwardly at the ends thereof.

8 is a first notch on one side of the cylindrical member 8G (side wall facing each other)
8Ga, 8Gb), a second notch 8H (having opposite side walls 8Ha, 8Hb) at the other end, and a protrusion 8J at the center of the boss facing the second notch 8H. An output member which is a core member and has a handle shaft 9 having a serration with which a handle (not shown) is engaged on one side, and the pinion 13 on the other side.
A bearing shaft 10 for bearing 12 is integrally formed.

In the present embodiment, a recess 8E is formed on the upper surface side of the core member 8, and the bias spring 7 is attached to the recess 8E.

The output member 12 has a pinion 13 supported by the support shaft 10,
First claw 14D 180 degrees apart (with sidewalls 14Da, 14Db)
And the second claw 14E are integrally formed, and the first claw 14D
Has two locking grooves 14Dc and 14Dd.

The core member 8 is rotatably supported on the handle shaft 9 by the bearing boss 1A of the housing 1 and is housed inside the first brake spring 3 and the second brake spring 5.

Then, the hook portion at one end of the first brake spring 3
3A and the hook portion at one end of the second brake spring 5
5A is locked in the locking grooves 14Dc and 14Dd of the first claw 14D which is loosely inserted in the space of the first cutout 8G. The hook portions 3B and 5B at the other end are arranged near the side walls 8Ha and 8Hb of the second notch 8H, respectively.

Further, the bias spring 7 has a recess 8E in the core member 8.
The hooks 7A and 7B are attached to both the second claw 14E loosely inserted in the space of the second cutout 8H and the projection 8J of the core member 8. As a result, the hook portions 3B and 5B at the other ends of the first and second brake springs 3 and 5, respectively, are held such that the distances between the side walls 8Ha and 8Hb of the second cutout 8H are equal.

When the brake mechanism having such a structure is incorporated into the seat up-down adjusting mechanism as described above, the output member 12 applies a counterclockwise rotational force in FIG. 9 to the first and second claws 14D and 14E. Tries to rotate counterclockwise. However, this is because the hook portion 3A of the first brake spring 3 is locked in the locking groove 14Dc of the first claw 14D,
The rotation of the output member 12 is prevented by the braking force due to the expanding action of the first brake spring 3.

In this state, the protrusion 8J of the core member 8 is biased to the neutral state by both hook portions 7A and 7B of the bias spring 7, so that the rattling of the core member 8, that is, the handle is suppressed.

In the state shown in FIG. 9, the handle or core member 8
Rotate the core member 8 regardless of whether it is rotated counterclockwise to raise the seat or rotated clockwise to lower the seat.
The movement is against the biasing force of the bias spring 7 via.

Then, when the rotation of the core member 8 while bending the bias spring 7 progresses, the side wall 8Ha or 8Hb of the second cutout 8H becomes the other end 3B of the first spring 3 or the second
The diameter of the spring 5 is reduced by coming into contact with one of the other ends 5B of the springs 5, and the core member 8 is allowed to rotate.

Further, when the core member 8 rotates, the side wall 8Gb or 8Ga of the first cutout 8G abuts the side wall 14Db or 14Da of the first claw 14D, and the output member 12 is rotated in a predetermined direction to move the sheet up and down. Let

In this embodiment, the same operation feeling can be obtained regardless of the direction of rotation of the handle, because the same action is obtained.

When a load is applied on the seat, the output member 12
Rotates in the clockwise direction, the second brake spring 5 having the hook portion 5A locked in the locking groove 14Dd of the first claw 14D is expanded, and the brake is immediately obtained.

Next, the tenth embodiment of the second aspect of the present invention will be described.
Shown in the figure.

This embodiment is different from the first embodiment in that
In this embodiment, both ends of the first and second brake springs 3 and 5 are locked to the first claw 14D, and the other end is the second.
The side walls 8Ha of the notch 8H are biased by the bias spring 7 so as to be equally spaced from the notches 8H and 8Hb, respectively, while this embodiment is the same as the embodiment shown in the first mode of the present invention. So that the core member 8 has a first notch
8GA (having opposite side walls 8GAa and 8GAb) is formed with a third notch 8GB (having opposite side walls 8GBa and 8GBb) which is expanded while having one side wall in common, and the first and second The arrangement of the brake springs is different.

That is, as shown in FIG. 10, the hook portion 3A at one end of the first brake spring 3 is brought into contact with the side wall 14Da of the first pawl 14D, and the hook portion 3B at the other end is formed of the first cutout 8GA. It is arranged near the side wall 8GAb.

Also, the hook portion 5A at one end of the second brake spring 5
Is locked in the locking groove 14De provided in the center of the first claw 14D, and the hook portion 5B at the other end is the third cutout 8GB side wall 8GB
It is placed near a.

Then, as in the previous embodiment, the bias spring 7 is mounted in the recess 8E of the core member 8, and both hook portions 7A and
7B is the second claw 14 that is loosely inserted in the space of the second notch 8H.
It is locked to both E and the projection 8J of the core member 8. As a result, due to the biasing force of the bias spring 7, the hook portions 3B and 5B at the other ends of the first and second brake springs 3 and 5 respectively have the side wall 8GAb and the third notch of the first notch 8GA. The side wall of 8GB is held so that it is evenly spaced from 8GBa.

Since the other structure is the same as that of the previous embodiment, the same parts are designated by the same reference numerals to avoid redundant description.

Thus, when the brake mechanism having such a configuration is incorporated in the seat up-down adjusting mechanism as described above, the output member 12 moves to the first position.
In FIG. 10, a counterclockwise rotating force is applied, and the first and second claws 14D and 14E try to rotate counterclockwise. However, this is because the hook portion 3A of the first brake spring 3 is in contact with the side wall 14Da of the first pawl 14D,
The rotation of the output member 12 is prevented by the braking force due to the diameter expansion action of the brake spring 3.

In this state, as described in the previous embodiment, the protrusion 8J of the core member 8 is biased to the neutral state by the hook portions 7A and 7B of the bias spring 7, so that the core member 8, that is, the rattling of the handle. Sticking is suppressed.

When the handle, that is, the core member 8 is rotated counterclockwise from the state shown in FIG. 10 to raise the seat, the protrusion 8J of the core member 8 causes the bias spring 7 to resist the urging force. The side wall 8GAb of the first notch 8GA comes into contact with the hook portion 3B at the other end of the first brake spring 3, and the diameter of the first brake spring 3 is reduced.

Further, when the core member 8 is rotated, the hook portion 3B of the first brake spring 3 is brought into contact with the side wall 14Db of the first pawl 14D, the output member 12 is rotated counterclockwise, and the seat is lifted.

On the contrary, when the core member 8 is rotated clockwise to lower the seat, first, the bias spring 7 is contracted by the projection 8J of the core member 8 as in the case of the upward movement, and further rotation causes the bias spring 7 to move to the first position. The side wall 8GBa of the three notches 8GB comes into contact with the hook portion 5B at the other end of the second brake spring 5 to reduce the diameter of the second brake spring 5.

Further, when the core member 8 rotates, the side wall 8GAa of the first cutout 8GA comes into contact with the hook portion 3A of the first brake spring 3 which is in contact with the side wall 14Da of the first pawl 14D. At the same time, the first claw 14D and thus the output member 12 are rotated clockwise, and the seat is lifted.

As described above, the core member 8 is always moved against the biasing force of the bias spring 7 or the first and second springs 3 and 5 regardless of the rotation of the handle in any direction. No rattling occurs, and good operation feeling is obtained.

When a load is applied on the seat, the output member 12
Tries to rotate in the clockwise direction, the second brake spring 5 in which the hook portion 5A at one end thereof is locked to the first claw 14D is expanded in diameter, and a braking force is immediately obtained. Further, in this embodiment, when the output member 12 rotates, the first member
Abut on the hook portion 3B of the brake spring 3 of
Since the brake spring 3 is also expanded in diameter, a braking force can be obtained here as well, and the braking force doubles.

In addition, in all of the above-described embodiments, since the first and second brake springs having the same shape can be used, it is not necessary to prepare them separately, and the cost increase can be suppressed.

[Effects of the Invention] As is apparent from the above description, according to the present invention, a large braking force can be obtained, and rattling of the output member and the core, that is, the handle can be surely minimized, and the operation feeling thereof can be reduced. The ring can be improved.

[Brief description of drawings]

FIG. 1 is an exploded perspective view showing constituent parts of a first embodiment of the first mode of the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 1 is a side sectional view showing a second embodiment of the present invention, FIG. 4 is a sectional view taken along line IV-IV of FIG. 3, and FIG. 5 is an exploded perspective view showing a third embodiment of the first aspect of the present invention. 6 is a sectional view taken along line VI-VI in FIG. 5, FIG. 7 is an exploded perspective view showing a first embodiment of the second mode of the present invention, FIG. 8 is a side sectional view thereof, and FIG. 8 is a sectional view taken along line IX-IX in FIG. 8, and FIG. 10 is a sectional view showing a second embodiment of the second mode of the present invention. 1 ... Brake housing, 3 ... 1st brake spring, 5 ... 2nd brake spring, 7 ... Bias spring, 8 ... Core member, 8A, 8G, 8GA ... 1st notch, 8B,
8H ... second notch, 8GB ... third notch, 9 ... handle shaft, 12 ... output member, 13 ... pinion, 14 ... pawl, 14D ... first
Claws, 14E ... second claws, 14A, 14Dc, 14Dd, 14De ... engaging grooves.

Claims (2)

[Claims] 1. A core member, in which at least one brake spring is mounted in the housing so as to be capable of pressure contact with an inner wall of the housing, and a core member provided with a notch and rotated by an operating means is rotated inside the brake spring. An output member having a claw that is housed as much as possible and that is loosely inserted in the notch space of the core member is rotatably provided, and one end of the at least one brake spring is in contact with the notched side wall of the core member. And one end of which is locked to the core member and the other end of which is disposed between the pawl and one end of the brake spring is locked to one end of the at least one brake spring. And a bias spring for urging the one end wall of the cutout of the core member in a direction to abut one end of the at least one brake spring. Over key mechanism. 2. A first and a second brake springs are mounted in the housing so as to be capable of press-contacting an inner wall of the housing, and a core member rotated by an operating means is provided inside the first and the second brake springs. An output member that has a claw portion that is rotatably housed in the core member and that is loosely inserted in the space of the cutout of the core member, and that outputs one end of each of the first and second brake springs to the output. The claw portion of the member is arranged to be engageable with each other, and the other end thereof is arranged to be able to abut on the notched side wall of the core member, and further, both ends are engaged with the output member and the core member and the The breaker is provided with a bias spring for urging the output member in a direction in which a gap between the other end of each of the first and second brake springs and the notched side wall of the core member is substantially equal. Mechanism.