JPH0673476U - Spring brake device - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a spring brake device capable of reducing weight and manufacturing cost. [Structure] The operation handle shaft 10 is integrally formed of a synthetic resin material mixed with a reinforcing material, and the operation handle attachment portion 12 is provided on one side.
, The drive gear mounting portion 13 is formed on the other side, and the core 11 housed in the brake drum portion 31 is formed on the intermediate portion. The operation handle mounting portion 1 is formed on the base portion of the core 11.
While forming the enlarged diameter portion 11b larger than the diameter of 2,
A plurality of recesses 11 are formed around the enlarged diameter portion 11b along the axis.
c is formed, and a concave portion 11 is formed on the side peripheral portion of the core 11.
forming d.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a spring brake device used for a vehicle seat lifter, a window regulator, or the like.

[0002]

[Prior art]

 Conventionally, as a spring brake device used for a seat lifter or the like, for example, as shown in FIG. 7, a torsion spring 2 is arranged in a brake drum 1 so as to be in pressure contact with an inner wall 1a of the brake drum 1. Then, with respect to the rotational force from the drive gear side, the claw member 3 provided integrally with the drive gear presses the hook portions 2a and 2b formed at both ends of the torsion spring 2 and the outside of the torsion spring 2 Since the diameter is expanded, the pressure contact force of the torsion spring 2 against the inner wall 1a of the brake drum 1 is increased, and the rotation of the drive gear is blocked.

On the other hand, with respect to the rotational force from the core 5 side provided on the operation handle shaft 4, the hook 5 of the torsion spring 2 is hooked by the side end 5b or 5c of the cutout recess 5a formed on the outer peripheral surface of the core 5. The portion 2b or 2c is pressed, and the torsion spring 2 receives a force in the direction of reducing the outer diameter, whereby the core 5 becomes rotatable. That is, the rotation from the operation handle shaft 4 can be transmitted to the drive gear side via the torsion spring 2 and the pawl member 3.

In the spring brake device described above, the core 5 is integrally attached to the operation handle shaft 4 by the attachment structure shown in FIG. 8 or 9.

In the mounting structure shown in FIG. 8, a synthetic resin core 5 is integrally mounted on a metal operation handle shaft 4 by molding. In this mounting structure, when the rotation is transmitted from the operation handle shaft 4 side to the drive gear side, the spring force of the torsion spring 2 acts on the core 5, so that the core 5 does not rotate with respect to the operation handle shaft 4. In addition, the core mounting portion of the operation handle shaft 4 is provided with knurling 4a as a rotation stopping means.

In FIG. 8, the operation handle shaft 4 is set so that an operation handle is attached to one end side 4b and a drive gear is attached to the other end side 4c.

Further, in the mounting structure shown in FIG. 9, a core 5 made of aluminum alloy or zinc alloy is integrally mounted by die casting on a metal operation handle shaft 4, and the core 5 As a rotation preventing means, a polyhedron, for example, a hexagonal rotation preventing process 4d is applied to the core mounting portion of the operation handle shaft 4.

[0008]

[Problems to be solved by the device]

 However, in the above-mentioned spring brake device, the rotation stopping means of the core 5 for knurling the operation handle shaft 4 shown in FIG. 8 has a problem that the manufacturing cost becomes high, and the operation handle shown in FIG. The rotation preventing means of the core 5 which performs the rotation preventing process 4d on the shaft 4 has a problem that the manufacturing cost is increased and the weight is increased.

The present invention has been made to solve the above-mentioned problems of the prior art, and its object is to provide a spring brake device capable of reducing the weight and the manufacturing cost. Especially.

[0010]

[Means for Solving the Problems]

 In order to achieve the above-mentioned object, the present invention installs an operation handle shaft having a core in an intermediate part on a brake drum so that the core is inside the brake drum part, and A torsion spring is arranged between the outer circumference of the torsion spring and the inner wall of the brake drum so as to be pressed against the inner wall of the brake drum, and the hook portions formed at both ends of the torsion spring are exposed in the notched concave portion formed on the outer peripheral surface of the core. Further, the operation handle is fixed to one side of the operation handle shaft, and the drive gear is rotatably supported on the other side, and a claw member integrally formed with the drive gear is provided between both hooks of the torsion spring. It is possible to rotate the drive handle by rotating the operation handle to reduce the diameter of the torsion spring. In this spring brake device, the operation handle shaft is integrally molded of a synthetic resin material mixed with a reinforcing material, the operation handle attachment part is on one side, the drive gear attachment part is on the other side, and the brake part is in the middle part. Each of the cores is configured to be housed in the drum portion, and a diametrically expanded portion having a diameter larger than the diameter of the operation handle attachment portion is formed at the base of the core, and a plurality of diametrically expanded portions are provided around the diametrically expanded portion along the axis. It is characterized by forming a number of recesses and further forming recesses on the side peripheral portion of the core.

[0011]

[Action]

 Since the core of the operation handle shaft is integrally molded with a synthetic resin material mixed with a reinforcing material, there is no need to perform a separate process unlike the conventional case. As a result, the manufacturing cost can be reduced and the weight can be reduced.

Further, the spring force of the torsion spring acting on the core can be sufficiently coped with by the expanded diameter portion formed on the base portion of the core. Therefore, it is possible to sufficiently secure the same strength as the conventional product.

Furthermore, since the sink marks at the time of molding can be eliminated by the recesses formed in the expanded diameter portion and the side peripheral portion of the core, deterioration of the strength of the operation handle shaft can be prevented.

[0014]

【Example】

 The present invention will be described below based on the embodiments shown in the drawings.

FIG. 1 is an exploded perspective view of a spring brake device, FIG. 2 is a longitudinal sectional view of the same, FIG. 3 is a front view of an operating handle shaft, and FIG. 4 is a side view of IV-IV in FIG. 5, FIG. 5 is a sectional view taken along the line V-V of FIG. 4, and FIG. 6 is an operation explanatory view of the spring brake device.

In the figure, E is a spring brake device, in which an operating handle shaft 10 having a core 11 in an intermediate portion is attached to a brake drum 30 so that the core 11 is inside a brake drum portion 31. The torsion spring 40 is arranged between the portion 31 and the core 11 so as to be pressed against the inner wall 31a of the brake drum portion 31 at the outer periphery thereof, and the hook portions 40a and 40b formed at both ends of the torsion spring 40 are provided at the core. The drive gear 50 has a cutout recess 11a formed on the outer peripheral surface of the drive gear 11, and an operation handle 20 fixed to one side of the operation handle shaft 10 and a drive gear 50 rotatably supported on the other side. A claw member 51 formed integrally with is inserted between both hooks 40a and 40b of the torsion spring 40. By rotating the operation handle 20, the diameter of the torsion spring 40 is reduced so that the drive gear 50 can be rotated.

According to the present invention, in particular, the operation handle shaft 10 is integrally formed of a synthetic resin material mixed with a reinforcing material, the operation handle attachment portion 12 is provided on one side, the drive gear attachment portion 13 is provided on the other side, and the intermediate portion is formed. Each of the cores 11 housed in the brake drum portion 31 is formed on the base of the core 11, and an enlarged diameter portion 11b larger than the diameter of the operation handle attachment portion 13 is formed on the base portion of the core 11 and the enlarged diameter portion 11b is formed. It is characterized in that a plurality of concave portions 11c are formed along the axis and the concave portions 11d and 11e are formed in the side peripheral portion of the core 11.

Further, the structure of the present invention will be described in detail.

The brake drum 30 includes a brake drum portion 31 and a flange portion 32. The flange portion 32 is fixed to, for example, a seat side frame 33 of a seat lifter. The brake drum portion 31 is formed with a first braking surface 31a, which is an inner wall, and a cylindrical second braking surface 31b, which is concentrically arranged inside the first braking surface 31a. Further, in the brake drum portion 31, the core 11 of the operation handle shaft 10, the torsion spring 40 that is in pressure contact with the first braking surface 31a, and the sub torsion spring 41 that is in pressure contact with the second braking surface 31b are housed, respectively. The hook portions 40a, 40b and 41a, 41b formed at both ends of the spring 40 and the sub torsion spring 41 face between the side end portions 11m, 11n formed in the cutout recess 11a of the core 11.

The operation handle shaft 10 is integrally formed of a reinforcing material, for example, a synthetic resin material mixed with glass fiber. A spline key 12a is formed on the operation handle attachment portion 12 formed on one side of the operation handle shaft 10, and the operation handle 20 is press-fitted therein.

A drive gear 50 integrally formed with a claw member 51 is rotatably supported by a drive gear mounting portion 13 formed on the other side of the operation handle shaft 10. The drive gear 50 is always meshed with a sector-shaped sector gear 61 provided in the lifter mechanism 60, and is configured to move the seat frame of the seat lifter up and down by forward or reverse rotation of the drive gear 50. Further, one hook portion 41b of the sub torsion spring 41 is engaged with the engaging groove 51a formed in the claw member 51, and this hook portion 41b, when the rotational force is input from the drive gear 50 side, It is set so that it acts in the winding direction of the sub torsion spring 41 and its outer diameter is reduced.

The core 11 is formed integrally with the intermediate portion of the operating handle shaft 10. The expanded diameter portion 11b formed at the base of the core 11 has a plurality of arc-shaped arcs along its axis in the circumferential direction, for example, over the entire area. Is formed with a concave portion 11c. Further, the core 11 is formed with a fitting portion 11g, which is fitted to the inner wall of the second braking surface 31b, on the side opposite to the operation handle attaching portion, which is continuous with the expanded diameter portion 11b. The diameter of 11g is set to be slightly larger than the diameter of the expanded diameter portion 11b.

On the side peripheral portion of the core 11, a concave portion 11d is formed on the side of the expanded diameter portion 11b in the circumferential direction, for example, over the entire area, and the depth thereof is the axial width a of the core 11 (see FIG. 3). ) Of at least 2/4 to 3/4.

Further, on the side peripheral portion of the core 11, a concave portion 11e is formed on the drive gear mounting portion 13 side in the circumferential direction, for example, over the entire area, and the depth thereof is the axial width a of the core 11. It is set to at least 2/5 to 4/5.

Further, on the side surface of the core 11 on the drive gear mounting portion 13 side, an escape groove 11f is formed outside the recess 11e over the entire circumference.

In the spring brake device E configured as described above, when the operating handle shaft 10 is rotated counterclockwise in FIG. 6 by operating the operating handle 20, the side end portion of the cutout recess 11 a of the core 11 is The hook portion 40b of the torsion spring 40 is pressed by 11n, and accordingly, the diameter of the torsion spring 40 is reduced and acts on the first braking surface 31a in a loosening direction, and the claw member 51 causes the sub torsion spring 41 to move. The diameter increases and acts on the second braking surface 31b in a loosening direction. As a result, the rotational power of the operating handle shaft 10 is transmitted to the drive gear 50 via the core 11 and the pawl member 51.

Further, when the operation handle shaft 10 is rotated in the timewise direction in FIG. 6 by operating the operation handle 12, the side end 11m of the cutout recess 11a of the core 11 presses the hook portion 40a of the torsion spring 40. As a result, the diameter of the torsion spring 40 decreases and acts on the first braking surface 31a in a loosening direction. Other functions are the same as those when the operation handle shaft 10 is rotated counterclockwise.

Next, at the time of seating, when the load of the occupant is input to the drive gear 50 side as rotational power in the direction of arrow b in FIG. 6 via the sector gear 61, the pawl member 51 integrated with the drive gear 50 is used. As a result, the diameter of the sub torsion spring 41 is reduced, and the sub torsion spring 41 comes into strong pressure contact with the second braking surface 31b to exert a braking action. That is, the braking force is exerted by the spring force of the sub torsion spring 41, and the rotation of the drive gear 50 can be prevented.

Further, at this time, since the pawl member 51 is engaged with the sub torsion spring 41, there is no play, and the backlash of the drive gear 50 can be prevented.

Further, when an excessive load (load exceeding the braking force of the sub torsion spring 41) is input to the drive gear 50, the claw member 51 integrated with the drive gear 50 rotates in the direction of arrow b (see FIG. 6). As the sub-torsion spring 41 is moved and presses the terminal 40a of the torsion spring 40 at the same time as the sub-torsion spring 41, the diameter of the sub-torsion spring 41 is reduced and the diameter of the torsion spring 40 is expanded to increase the first and second braking surfaces 31a, 31b. It comes into strong pressure contact with and the braking action comes to work. As a result, when an excessive load is input to the drive gear 50, both the braking force of the torsion spring 40 and the braking force of the sub torsion spring 41 can be obtained at the same time.

Here, since the operation handle shaft 10 has the core 11 integrally formed with a synthetic resin material mixed with glass fiber, it is necessary to perform the knurling process 4a or the rotation stopping process 4d as in the conventional case. There is no. This makes it possible to reduce manufacturing costs and weight.

Further, the spring force of the torsion spring 40 and the sub torsion spring 41 acting on the core 11 can be sufficiently dealt with by the enlarged diameter portion 11 b formed at the base of the core 11. Therefore, it is possible to sufficiently secure the strength equivalent to that of the conventional product.

Further, the recesses 11c, 11d, and 11e formed in the expanded diameter portion 11b and the side peripheral portion of the core 11 can eliminate sink marks during molding, thus preventing deterioration of the strength of the operating handle shaft 10. You can

If the depth of the recessed portion 11d exceeds 3 / 4a (a is the axial width of the core 11 shown in FIG. 3), the strength deteriorates. If the depth is less than 2 / 4a, sink marks occur during molding. However, it is preferable to set it to 2 / 4a to 3 / 4a. Similarly, the depth of the recess 11e is preferably set to 2 / 5a to 4 / 5a.

[0035]

[Effect of device]

 As described above, according to the present invention, since the operation handle shaft has the core integrally formed with the synthetic resin material mixed with the reinforcing material, the manufacturing cost can be reduced and the weight can be reduced.

Further, the spring force of the torsion spring acting on the core can be sufficiently dealt with by the enlarged diameter portion. Therefore, it is possible to sufficiently secure the strength equivalent to that of the conventional product.

Further, the recesses formed in the expanded diameter portion and the side peripheral portion of the core can eliminate sink marks at the time of molding, so that deterioration of the strength of the operation handle shaft can be prevented.

[Brief description of drawings]

FIG. 1 is an exploded perspective view of a spring brake device according to the present invention.

FIG. 2 is likewise a longitudinal cross-sectional explanatory view of a main part.

FIG. 3 is an explanatory front view of an operation handle shaft.

FIG. 4 is an explanatory view taken along the line IV-IV in FIG.

5 is a cross-sectional view taken along the line VV of FIG.

FIG. 6 is an operation explanatory view of the spring brake device according to the present invention.

FIG. 7 is a cross-sectional explanatory view showing an outline of a spring brake device according to a conventional example.

8 is a cross-sectional explanatory view showing a core mounting structure for the operation handle shaft shown in FIG. 7. FIG.

9 is a cross-sectional explanatory view showing another embodiment of the core mounting structure of FIG.

[Explanation of symbols]

 E Spring Brake Device 10 Operation Handle Shaft 11 Core 11a Notch Recess 11b Expanded Diameter 11c Recess 11d Recess 11e Recess 12 Operation Handle Attachment 13 Drive Gear Attachment 20 Operation Handle 30 Brake Drum 31 Brake Drum 31a Inner Wall (First Braking Surface) ) 40 torsion spring 40a hook part 40b hook part 41 sub torsion spring 41a hook part 41b hook part 50 drive gear 51 claw member

Claims (3)

[Scope of utility model registration request] 1. An operation handle shaft having a core in an intermediate portion is attached to a brake drum so that the core is inside the brake drum portion, and a torsion spring is provided between the brake drum portion and the core. The outer periphery is arranged so as to be in pressure contact with the inner wall of the brake drum, and the hook portions formed at both ends of the torsion spring are exposed in the notched recesses formed in the outer peripheral surface of the core. The operation handle is fixed to one side, the drive gear is rotatably supported on the other side, and a claw member integrally formed with this drive gear is inserted between both hooks of the torsion spring to remove the operation handle. A spring brake device that rotates the drive gear by rotating the torsion spring to reduce its diameter. The operation handle shaft is integrally formed of a synthetic resin material mixed with a reinforcing material, and the operation handle mounting portion is housed on one side, the drive gear mounting portion is housed on the other side, and the brake drum portion is housed in the middle portion. Each of the cores is formed and configured, and a diameter-increased portion having a diameter larger than that of the operation handle attachment portion is formed on a base portion of the core,
A plurality of recesses are formed along the axis around the expanded diameter portion,
Further, the spring brake device is characterized in that a recess is formed in a side peripheral portion of the core. 2. The recess formed in the side peripheral portion of the core,
The spring brake device according to claim 1, wherein the spring brake device is formed on the enlarged diameter side of the core and has a depth of at least 2/4 to 3/4 of the axial width of the core. 3. The recess formed in the side peripheral portion of the core,
The spring brake device according to claim 1, wherein the spring brake device is formed on the drive gear mounting side of the core and has a depth of at least 2/5 to 4/5 of the axial width of the core.