JP5417826B2 - Brake mechanism of hoisting machine - Google Patents

Description

  The present invention relates to a brake mechanism for an elevator hoist.

  The brake mechanism provided in the elevator hoist includes, for example, a cylindrical brake drum that rotates in conjunction with the sheave, and a brake arm arranged outside the brake drum is attached to the outer peripheral wall of the brake drum. There are some which generate a frictional force necessary for braking the sheave between the brake arm and the outer peripheral wall of the brake drum by being pressed.

  FIG. 3 is a partial cross-sectional view showing an example of a conventional general elevator hoisting machine. As shown in FIG. 3, the brake drum 1 is formed in a substantially cup shape, and a stator 3 fixed to the frame 2 is disposed in the cup-shaped gap (between the rotor core and the outer peripheral wall 7). Has been. A permanent magnet 4 is fixed in the cup-shaped gap of the brake drum 1 (fixed so as to face the stator 3 in FIG. 3), and the permanent magnet 4 is applied by applying an electric current to the stator 3. A magnetic force is generated between the brake drum 1 and the stator 3, and torque is generated in the brake drum 1 and the sheave (not shown).

  When braking the sheave (and the brake drum 1), the brake arm 5 provided on the radially outer side of the brake drum 1 is moved inward (brake drum 1 side) and is provided on the brake arm 5. By pressing the pressing surface 8 of the brake lining 6 against the outer peripheral wall 7 of the brake drum 1, a frictional force is generated between the pressing surface 8 of the brake lining 6 and the outer peripheral wall 7 of the brake drum 1, and the sheave (and The rotation of the brake drum 1) is braked.

In the elevator hoist as described above, the amount of elastic deformation of the brake drum 1 is reduced by fixing a reinforcing material having an elastic coefficient larger than that of the brake drum 1 to the outer peripheral wall 7 of the brake drum 1. It has been proposed to reduce the noise generated during braking caused by elastic deformation of the drum 1 (for example, Patent Document 1).
JP 2006-117342 A (paragraphs [0011] to [0012], FIG. 3)

  The brake drum 1 is formed in a substantially cup shape because it is necessary to dispose the stator 3 therein, and the outer peripheral wall 7 of the brake drum 1 is cantilevered (only on the opposite side of the frame 2 of the brake drum 1). The structure was supported at the bottom. In the case of the structure in which the outer peripheral wall 7 is cantilevered as described above, when the outer peripheral wall 7 is pressed against the brake lining 6 (the pressing surface 8) during braking, FIG. As shown in the partial cross-sectional view, the outer peripheral wall 7 of the brake drum 1 was bent toward the stator 3 (in FIG. 4, a state bent at an inclination angle θ). The deflection of the outer peripheral wall 7 decreases as it approaches the cantilever-supported side, and increases as it approaches the side that is not cantilever-supported. Therefore, along with the bending of the outer peripheral wall 7, the pressing surface 8 of the brake lining 6 and the outer peripheral surface of the outer peripheral wall 7 of the brake drum 1 are not kept horizontal and are distorted, and the brake drum 1 and the brake lining 6 The surface pressure of the outer peripheral wall 7 on the cantilever-supported side was large, and the opening end side was small.

  As a result, the brake torque becomes unstable, the life of the brake lining 6 decreases (the wear on the opposite side of the frame 2 is fast), and the brakes slide (friction between the outer peripheral wall 7 of the brake drum 1 and the brake lining 6). Problems such as an increase occurred.

  Further, in the case of a brake mechanism having an axial swing function in the brake arm 5, it is possible to keep the pressing surface 8 of the brake lining 6 and the outer peripheral surface of the outer peripheral wall 7 of the brake drum 1 horizontal during braking. The surface pressure between the outer peripheral wall 7 of the brake drum 1 and the brake lining 6 can be constant between the side supported by the cantilever and the side not supported by the cantilever, but the brake mechanism is complicated and the hoisting machine is large. There is a problem that the cost increases as the cost increases.

  As described above, in the brake mechanism of the hoisting machine having a structure in which the outer peripheral wall of the brake drum is cantilevered, the outer peripheral surface of the outer peripheral wall of the brake drum at the time of braking is used without using a new member. It is required to eliminate distortion with the pressing surface of the brake lining.

By pressing the outer peripheral wall of the cup-shaped brake drum with a brake lining fixed to the brake arm, a frictional force is generated between the outer peripheral surface of the outer peripheral wall and the pressing surface of the brake lining, A brake mechanism of a hoisting machine that brakes a sheave that rotates together with the brake drum, and the outer peripheral wall of the brake drum is formed in a tapered shape with an outer diameter approaching the opening end, and the pressing surface of the brake lining is The brake drum is characterized in that it is formed horizontally with the outer peripheral surface of the outer peripheral wall of the brake drum in a state where the outer peripheral wall of the brake drum is bent in the direction opposite to the pressing surface of the brake lining during braking .

By pressing the outer peripheral wall of the cup-shaped brake drum with a brake lining fixed to the brake arm, a frictional force is generated between the outer peripheral surface of the outer peripheral wall and the pressing surface of the brake lining, A brake mechanism of a hoisting machine that brakes a sheave that rotates together with the brake drum. The thickness of the brake lining is formed in a tapered shape as it approaches the opening end side of the outer peripheral wall. The outer peripheral surface is characterized by being formed horizontally with the pressing surface of the brake lining in a state where the outer peripheral wall of the brake drum is bent in the opposite direction to the pressing surface of the brake lining during braking .

As is apparent from the above description, according to the first and second aspects of the invention, the brake drum and the brake lining can be prevented from being deformed during braking, the brake torque can be stabilized, the life of the brake lining can be extended, and the brake sliding. The alignment time can be shortened.

According to the second aspect of the present invention, since it is easier to form the brake lining in a tapered shape than in the case where the outer peripheral wall of the brake drum is formed in a tapered shape, the machining time can be shortened.

  Hereinafter, the brake mechanism of the hoisting machine in the embodiment of the present invention will be described in detail based on the first and second embodiments.

  In the hoisting machine brake mechanism according to the first and second embodiments, at least one of the outer peripheral surface of the outer peripheral wall of the brake drum and the pressing surface of the brake lining has a friction surface on the opening end side of the brake drum except during braking. In this case, the outer peripheral surface of the outer peripheral wall and the pressing surface of the brake lining become horizontal while the outer peripheral surface is pressed and bent by the brake lining during braking.

[Embodiment 1]
1A (front view), FIG. 1B (cross-sectional view), and FIG. 1C (A-A cross-sectional view in FIG. 1A) are hoistings according to Embodiment 1 of the present invention. It is a schematic explanatory drawing which shows the brake mechanism of a machine. As shown in FIGS. 1 (B) and 1 (C), the hoisting machine of the first embodiment uses an inner rotor type motor, and the permanent magnet 4 provided in the rotating portion 9 is fixed. Opposed to the inner peripheral side of the stator 3 provided in the portion 10.

  The fixing portion 10 is provided in a circular shape in the same direction as the shaft portion from the frame 2, a shaft portion (not shown) that is erected from the frame 2 and formed integrally with the frame 2. The stator 3 is mainly configured. The stator 3 includes, for example, a stator core 3a formed by laminating a large number of steel plates and a winding 3b wound around the stator core 3a.

  The rotor core 11 of the rotating portion 9 is rotatably supported by the shaft portion via a bearing (not shown) and is disposed to face the frame 2 of the fixed portion 10. A sheave 12 is fixed to the opposite side of the frame 2 of the rotor core 11 (for example, fixed by a bolt or the like), and an elevator hoistway is provided in a V-shaped rope groove 12a formed on the outer peripheral surface of the sheave 12. A rope for suspending a car (not shown) that moves up and down is wound.

  A permanent magnet 4 is fixed to the outer periphery of the rotor core 11, and the permanent magnet 4 is disposed opposite to the stator 3 with a radial gap on the inner peripheral side. Further, a brake drum 1 formed in a cylindrical shape with a bottom or a substantially cup shape projects from the outer peripheral surface of the rotor core 11. Since the brake drum 1 is formed in a substantially cup shape, the outer peripheral wall 7 of the brake drum 1 is supported only on the sheave 12 side and has a cantilevered structure that is not supported on the anti-sheave 12 side. The stator 3 and the permanent magnet 4 are arranged on the radially inner side of the outer peripheral wall 7. The outer peripheral surface 17 of the brake drum 1 has a larger diameter than the rotor core 11, the sheave 12, and the permanent magnet 4.

  When a current is applied to the stator 3 of the fixed portion 10, a magnetic force is generated between the stator 3 and the permanent magnet 4, and the rotor core 11 that supports the permanent magnet 4 rotates. As the rotor iron core 11 rotates, the brake drum 1 formed integrally with the rotor iron core 11 and the sheave 12 fixed to the rotor iron core 11 rotate together. As the sheave 12 rotates, the car moves up and down through the rope wound around the rope groove 12a of the sheave 12.

  A pair of brake arms 5 are supported on the frame 2 via a rotation shaft 13 so as to be rotatable in the radial direction of the brake drum 1. One end side of the brake arm 5 is connected to one end side of a pair of opposing brake shafts 14, and a brake lining 6 that contacts and separates from the outer peripheral wall 7 of the brake drum 1 is attached to the other end side of the brake arm 5. The brake shaft 14 is inserted into an electromagnet 15 for releasing a braking force, and a brake spring 16 for applying a braking force is provided around the brake shaft 14.

  Therefore, when a current is applied to the electromagnet 15, the brake shaft 14 moves inward against the elastic force of the brake spring 16 due to the magnetic force of the electromagnet 15. 14) is moved inward. As a result, the brake arm 5 rotates about the rotation shaft 13 (the brake arm 5a rotates counterclockwise and the brake arm 5b rotates clockwise), and the brake lining fixed to the other end of the brake arm 5 is fixed. 6 is released from the outer peripheral wall 7 of the brake drum 1 and braking is released.

  On the other hand, when energization of the electromagnet 15 is stopped, the magnetic force of the electromagnet 15 disappears, and the brake shaft 14 moves to the outside by the elastic force of the brake spring 16. (The side connected to the brake shaft 14) moves outward. As a result, the brake arm 5 rotates around the rotation shaft 13 (the brake arm 5a rotates clockwise and the brake arm 5b rotates counterclockwise), and the brake lining fixed to the other end of the brake arm 5 is fixed. 6 is pressed against the outer peripheral wall 7 of the brake drum 1 to apply a braking force.

  In the brake mechanism of the hoisting machine formed as described above, the brake drum 1 of the first embodiment is configured such that the outer peripheral surface 17 of the outer peripheral wall 7 is an open end (cantilevered) as shown in FIG. The one whose side is inclined toward the brake lining 6 side is applied. Specifically, the outer peripheral wall 7 is formed in a tapered shape with the outer diameter becoming larger as it approaches the open end (not cantilevered) side. The inclination angle α of the outer peripheral surface 17 formed in a tapered shape is an angle that is horizontal with the pressing surface 8 of the brake lining 6 in a state where the outer peripheral wall 7 of the brake drum 1 is bent toward the stator 3 side. That is, since the deflection of the outer peripheral wall 7 of the brake drum 1 during braking varies depending on the material of the brake drum 1 and the thickness of the outer peripheral wall 7, the inclination angle α that forms the brake drum 1 in a tapered shape is determined by the brake drum 1 Design appropriately according to the material and thickness of 1. The inclination angle of the inner peripheral surface of the outer peripheral wall 7 may or may not be horizontal with the outer peripheral surface 17.

  By configuring as described above, the opening end side of the outer peripheral surface 17 of the outer peripheral wall 7 is inclined at an angle α toward the brake lining 6 side except during braking, but the outer peripheral wall 7 of the brake drum 1 is used during braking. Is pressed by the brake lining 6 and the outer peripheral wall 7 of the brake drum 1 is bent, whereby the outer peripheral surface 17 of the outer peripheral wall 7 and the pressing surface 8 of the brake lining 6 become horizontal.

  As a result, at the time of braking, there is no distortion between the outer peripheral surface 17 of the outer peripheral wall 7 and the pressing surface 8 of the brake drum 6, and the surface pressure between the outer peripheral surface 17 and the pressing surface 8 is the side where the cantilever is supported. The opening end side is also constant, the brake torque is stabilized, the life of the brake lining 6 is extended (the wear on the sheave 12 side is not quickly worn), and the brakes are rubbed together (the outer peripheral wall 7 of the brake drum 1 and the brake lining 6 (Friction) time can be shortened.

Moreover, since it is not necessary to provide the brake arm 5 with an axial swing function and to provide the brake drum 1 with a reinforcing material, it is possible to suppress the complexity of the brake mechanism and the enlargement of the hoisting machine, It becomes possible to suppress an increase in cost.
[Embodiment 2]
FIG. 2 shows another example of the brake mechanism of the hoisting machine according to the second embodiment, and is a cross-sectional view taken along the line AA of FIG. Since the basic configuration of the hoisting machine is the same as the configuration described in the first embodiment, detailed description is omitted using the same reference numerals.

  As the pressing surface 8 of the brake lining 6 according to the second embodiment, an anti-sheave (open end of the outer peripheral wall 7) side is inclined toward the brake drum 1 side. Specifically, the brake lining 6 increases in thickness as it approaches the frame 1 side, and is formed in a tapered shape. The inclination angle β formed in a tapered shape is an angle at which the outer peripheral surface 17 of the outer peripheral wall 7 and the pressing surface 8 of the brake lining 6 become horizontal in a state where the outer peripheral wall 7 of the brake drum 1 is bent. That is, since the bending of the outer peripheral wall 7 of the brake drum 1 during braking varies depending on the material of the brake drum 1 and the thickness of the outer peripheral wall 7, the inclination angle β that forms the brake lining 6 in a tapered shape is determined by the brake drum Design appropriately according to the material and thickness of 1. Note that the brake arm 5 and the fixing surface of the brake arm 5 and the brake lining 6 may or may not be horizontal with the pressing surface 8.

  By configuring as described above, the thickness of the brake lining 6 increases as it approaches the frame 2 side except during braking, and the pressing surface 8 of the brake lining 6 is inclined at an angle β toward the brake drum 1 side. During braking, the outer peripheral wall 7 of the brake drum 1 is pressed against the brake lining 6 and the outer peripheral wall 7 of the brake drum 1 is bent, so that the outer peripheral surface 17 of the outer peripheral wall 7 and the pressing surface of the brake lining 6 are deformed. 8 becomes horizontal.

  As a result, during braking, there is no distortion between the outer peripheral surface 17 of the outer peripheral wall 7 and the pressing surface 8 of the brake lining 6, and the surface pressure between the outer peripheral surface 17 and the pressing surface 8 is cantilevered. The opening end side is constant, the brake torque is stabilized, the life of the brake lining 6 is extended (the wear on the sheave 12 side is not quickly worn), and the brakes are rubbed together (the outer peripheral wall 7 of the brake drum 1 and the brake lining 6 (Friction) time can be shortened.

  Moreover, since it is not necessary to provide the brake arm 5 with an axial swing function and to provide the brake drum 1 with a reinforcing material, it is possible to suppress the complexity of the brake mechanism and the enlargement of the hoisting machine, It becomes possible to suppress an increase in cost.

  Furthermore, it is easier to form the brake lining 6 in a tapered shape as in the second embodiment than in the case where the outer peripheral wall 7 of the brake drum 1 is formed in a tapered shape as in the first embodiment. Shortening is possible.

  Although the present invention has been described in detail only for the specific examples described above, it is obvious to those skilled in the art that various changes and modifications are possible within the scope of the technical idea of the present invention. Such variations and modifications are naturally within the scope of the claims.

  For example, in the first and second embodiments, the brake mechanism of the hoisting machine having a specific configuration has been described in detail. However, any structure can be applied as long as the outer peripheral wall of the brake drum is cantilevered.

BRIEF DESCRIPTION OF THE DRAWINGS Schematic explanatory drawing which shows the brake mechanism of the hoisting machine in Embodiment 1. FIG. Schematic explanatory drawing which shows the brake mechanism of the hoisting machine in Embodiment 2. FIG. The fragmentary sectional view which shows an example of a general elevator hoisting machine. The fragmentary sectional view which shows the general elevator hoisting machine at the time of braking.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Brake drum 5 ... Brake arm 6 ... Brake lining 7 ... Outer peripheral wall 8 ... Pressing surface 11 ... Rotor core 12 ... Sheave 13 ... Rotating shaft 17 ... Outer peripheral surface

Claims (2)

By pressing the outer peripheral wall of the cup-shaped brake drum with a brake lining fixed to the brake arm, a frictional force is generated between the outer peripheral surface of the outer peripheral wall and the pressing surface of the brake lining, A brake mechanism of a hoisting machine that brakes a sheave that rotates together with a brake drum,
The outer peripheral wall of the brake drum is formed in a tapered shape that increases as the outer diameter approaches the open end,
The brake lining pressing surface is formed horizontally with the outer peripheral surface of the outer peripheral wall of the brake drum in a state where the outer peripheral wall of the brake drum is bent in the opposite direction to the pressing surface of the brake lining during braking . The brake mechanism of the upper machine. By pressing the outer peripheral wall of the cup-shaped brake drum with a brake lining fixed to the brake arm, a frictional force is generated between the outer peripheral surface of the outer peripheral wall and the pressing surface of the brake lining, A brake mechanism of a hoisting machine that brakes a sheave that rotates together with a brake drum,
The thickness of the brake lining is formed into a thick taper as it approaches the opening end side of the outer peripheral wall,
The outer peripheral surface of the outer peripheral wall of the brake drum is formed horizontally with the pressing surface of the brake lining with the outer peripheral wall of the brake drum being bent in the opposite direction to the pressing surface of the brake lining during braking . The brake mechanism of the upper machine.

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