WO2014185137A1 - Brake device for hoisting machine - Google Patents

Abstract

　Provided is a novel brake device for a hoisting machine wherein a deformable elastic body is used to suppress movement speed of a movable iron core and muffle collision sounds. The elastic body is designed so as to deform in a compressing manner by moving from a designated position in the movement direction of the movable iron core without being compressed to a designated position in the movement direction of the movable iron core. Collision noises are reduced due to the elastic body being compressed and the operating speed of the movable iron core being reduced as the movable iron core moves. In addition, the elastic body bulges in a circumferential direction by compressing and the elastic body comes in contact with the movable iron core, whereby vibration of the movable iron core can be damped.

Description

Brake device for hoisting machine

The present invention relates to a hoisting machine brake device used in a hoisting machine for moving an elevator car in a hoistway, and more particularly, a novel hoisting system that reduces noise generated when braking or releasing braking. The present invention relates to a machine brake device.

In recent elevator systems, in order to reduce the height of the building, a machine room for storing machinery such as a hoisting machine is not provided in the upper part of the hoistway, and so-called machine room-less machines are provided in the hoistway. Elevator systems are widespread.

In the case of this machine room-less elevator system, all devices including the hoisting machine that has been installed in the machine room are installed in the hoistway. There are various configurations for installing the hoisting machine in the hoistway, but in order to install the hoisting machine in a relatively narrow gap between the carriage and the hoistway wall, it is installed so as to face the hoistway wall. A hoisting machine is required. The thin hoist is firmly fixed to the hoistway wall with bolts or the like.

As a conventional hoisting machine, for example, a stator is formed integrally with a housing on an outer peripheral portion of a fixed main shaft supported by a housing and is rotatably attached to one end of the fixed main shaft via a bearing. It is known that a rotor is integrally formed on the outer peripheral portion of the sheave, and an electric motor portion is configured by the rotor and the stator that are arranged to face each other.

When operating the elevator system, the car is moved up and down through the main rope wound around the sheave when the sheave is rotated by the motor. On the contrary, when the operation is stopped, energization to the electric motor unit is stopped and the brake lining is pressed against the brake drum provided integrally with the sheave by the hoisting machine brake device to perform braking.

The hoisting machine brake device is configured to operate based on the electromagnetic attraction force of the electromagnetic coil provided on itself and the restoring force of the braking spring. During braking, the power supply of the electromagnetic coil is cut off, and braking is applied by pressing the brake lining against the brake drum as the braked body by the restoring force of the braking spring. At that time, the brake lining collides with the brake drum at a high speed due to the restoring force of the brake spring and generates a loud collision sound. Conversely, when releasing the brake, power is supplied to the electromagnetic coil to attract the moving iron core electromagnetically, and the brake lining is separated from the brake drum. At this time, the moving iron core collides with the fixed iron core at a high speed. A loud collision sound.

And, since the hoisting machine is fixed to the wall surface of the hoistway, the above-mentioned collision sound often leaks from the hoistway to the outside. In particular, in a machine room-less elevator system, the hoistway and the living space are close to each other, and the collision sound can easily propagate, which may lead to noise problems for residents, discomfort to passengers, and anxiety. For this reason, the hoisting machine brake device is strongly required to be quiet during operation. For example, what is described in JP-T-2009-537745 (Patent Document 1) is known as an object for improving quietness.

In the technique described in Patent Document 1, an O-ring made of rubber or the like is interposed between a movable iron core and a torque transmission sleeve that linearly moves the movable iron core to prevent contact between the two and the movable iron core and torque. It has been proposed to reduce the impact noise between the transmission sleeves.

In the above description, the case of a machine room-less elevator system has been described. However, it is important to improve quietness even in a machine room elevator system in which a hoisting machine or the like is installed in a machine room. Therefore, the present invention is directed to a hoisting machine brake device used in both a machine room-less elevator system and a machine room elevator system.

Special table 2009-537745

Incidentally, in Patent Document 1 described above, the movable iron core is disposed so as to face the torque transmission sleeve and the O-ring. The movable iron core moves through the O-ring in an operation state in which braking is performed and an operation state in which braking is released. For this reason, since the O-ring always maintains a sliding state with the movable iron core, a larger force is required to move the movable iron core. However, if the movable iron core is moved with a greater force, the collision noise during braking or braking will increase. Therefore, there has been a problem that the collision noise at the time of braking or braking is increased again.

An object of the present invention is to provide a novel hoisting machine brake device capable of suppressing a moving speed of a movable iron core and reducing a collision sound while suppressing an increase in force for moving the movable iron core. .

The feature of the present invention is that the elastic body is not compressed to a predetermined position in the moving direction of the movable core, and the elastic body is deformed and compressed by movement from the predetermined position in the moving direction of the movable core. . Further, as the movement of the movable iron core proceeds, the effects of suppressing the moving speed and reducing the noise of the collision sound are increased.

According to the present invention, as the movable iron core moves, the elastic body is compressed and the operating speed of the movable iron core is reduced, so that the collision noise is reduced. Accompanying this, the elastic body compresses and expands in the circumferential direction, and the elastic body presses the movable core, whereby the vibration of the movable core can be attenuated.

It is the schematic block diagram which showed the structure of the machine room less elevator system. 1 is a front view of a thin hoisting machine to which the present invention is applied. It is operation | movement explanatory drawing explaining the operation | movement of the brake device for hoisting machines, and explaining a braking state. It is operation | movement explanatory drawing explaining the operation | movement of the brake device for hoisting machines, and explaining the state which cancelled | released the braking. It is the top view which looked at the brake device for hoisting machines from the upper surface. It is sectional drawing which showed the longitudinal cross-section of the brake device for hoisting machines which becomes one Example of this invention. It is a disassembled perspective view which decomposes | disassembles the hoisting machine brake device shown to FIG. 4A, and shows a schematic structure. It is a principal part longitudinal cross-sectional view which shows the relationship between the movable iron core which is the principal part of a present Example, and an elastic body. It is a cross-sectional perspective view of the movable iron core which is the principal part of a present Example. It is a characteristic view which shows the relationship between the damping force of an elastic body, silence, braking force, and physique.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. However, the present invention is not limited to the following embodiments, and various modifications and application examples are included in the technical concept of the present invention. Is also included in the range.

First, before explaining an embodiment of the present invention, a schematic configuration of a machine room-less elevator system will be described. FIG. 1 is a diagram for explaining a general configuration of a machine room-less elevator, and components constituting the machine room-less elevator are accommodated in a hoistway provided in a building.

The elevator system includes a car 1, a counterweight 2 and a hoisting machine 3 as main components. A pulley 1A is attached to the lower part of the car 1, and a pulley 2A is attached to the counterweight 2, A sheave 6 is attached to the rotating shaft of the upper machine 3 (= the rotating shaft of the electric motor). Here, although the hoisting machine 3 is configured to be attached to a beam fixed near the top of the hoistway, the hoisting machine 3 may be configured to be placed on the floor of the bottom of the hoistway.

One end of the main rope 5 is attached to the upper wall surface of the hoistway. Starting from this one end, the upper part of the hoistway is passed through the pulley 2A of the counterweight 2, the sheave 6 of the hoisting machine 3, and the pulley 1A of the car 1. The other end is attached to the wall. This roping is called 2-to-1 roping, and the hoisting force of the hoisting machine 3 is reduced using the principle of a moving pulley.

A hoisting machine brake device 4 is mounted on the upper and lower sides of the hoisting machine 3, and a brake lining provided on the hoisting machine brake device 4 is pressed against a brake drum 7 fixed to the sheave 6. The brake is applied. In general, a shock absorber for buffering the impact caused by the collision of the counterweight 2 is installed in the lower part of the counterweight 2, but a buffer for buffering the shock caused by the collision of the car 1 is also provided below the car 1. A vessel is installed.

In such an elevator system, an operation command is given to an electric motor, a brake device, or the like of the hoisting machine 3 by a controller (not shown), and the car 1 is moved up and down toward a predetermined level of the building by the operation command. A stop operation is performed.

FIG. 2 shows an external configuration of the brake device 4 provided in the hoisting machine 3, and the brake device 4 is arranged facing the brake drum 7 with an interval of 180 °. That is, the brake device 4 is firmly fixed to the hoisting machine 3 by the mounting bracket 8 and the mounting bolts 9A and 9B on the upper side and the lower side of the thin hoisting machine 3 configured in a square shape. A brake shoe 10 is fixed to the front end side of the brake device 4, and the brake shoe 10 projects toward the brake drum 7 or is pulled back. When the brake shoe 10 protrudes toward the brake drum 7, braking is applied to the brake drum 7, and when the brake shoe 10 is pulled back from the brake drum 7, braking of the brake drum 7 is released. The detailed structure and operation state of the brake device 4 will be described with reference to FIGS. 3A and 3B.

3A and 3B, the brake device 4 mainly includes a fixed iron core 11, an electromagnetic coil 12, a brake spring 13, a movable iron core 14, and a brake shoe 10. The fixed iron core 11 made of a magnetic material such as iron is formed in the shape of a flat quadrangular prism that is square when viewed from above. An electromagnetic coil 12 for generating a magnetic force is housed inside the fixed iron core 11, and a braking spring 13 is disposed inside the electromagnetic coil 12.

A movable iron core 14 is movably disposed on the side of the fixed iron core 11 facing the brake spring 13, and the movable iron core 14 is guided by a guide portion (not shown) formed on the guide bolt 15 so as to be movable. ing. The movable iron core 14 is formed in a quadrangular shape like the shape of the fixed iron core 11. A fixing nut 16 for restricting the maximum displacement of the movable iron core 14 is screwed to the end portion of the guide bolt 15, whereby the movable iron core 14 is constantly urged toward the maximum displacement side by the brake spring 13. A brake shoe 10 is disposed on the opposite side of the movable iron core 14 on the side where the fixed iron core 11 is located, and this brake shoe 10 is fixed integrally with the movable iron core 14 by a connecting rod 10A. A brake lining 17 for braking the brake drum 7 is fixed to the tip of the brake shoe 10.

In the configuration as described above, when electric power is applied to the electromagnetic coil 12, the ionization coil 12 generates a magnetic force in the fixed iron core 11, and accordingly, the movable iron core 14 resists the elastic force of the brake spring 13. 11 is sucked. On the other hand, when the power supply to the electromagnetic coil 12 is interrupted, the ionization coil 12 cannot generate a magnetic force in the fixed iron core 11, and accordingly, the movable iron core 14 is fixed by the elastic force of the brake spring 13. It operates to move away from the iron core 11. Thus, the brake device 4 is configured to always work on the safe side in order to cope with a power failure or an abnormal state. In other words, braking is applied by cutting off the electric power.

Therefore, when the hoisting machine 3 is braked by the brake device 4, the power supplied to the electromagnetic coil 12 from a controller (not shown) may be cut off as shown in FIG. 3A. When the electric power is cut off in this way, the electromagnetic coil 12 and the fixed iron core 11 cannot generate magnetic force, and the movable iron core 14 moves away from the fixed iron core 11 by the elastic force of the brake spring 13, and the brake shoe 10. Move with this. Since the brake lining 17 is fixed to the tip of the brake shoe 10, the brake lining 17 is strongly pressed against the brake drum 7, the rotation of the brake drum 7 is stopped, and as a result, the hoisting machine 3 is braked. It is what

On the other hand, when the braking of the hoisting machine 3 by the brake device 4 is released, power may be supplied to the electromagnetic coil 12 from a controller (not shown) as shown in FIG. 3B. When electric power is supplied in this way, the electromagnetic coil 12 and the fixed iron core 11 can generate a magnetic force, and the movable iron core 14 moves so as to be attracted to the fixed iron core 11 against the elastic force of the brake spring 13. The brake shoe 10 also moves accordingly. For this reason, the brake lining 17 is separated from the brake drum 7, and as a result, the braking of the hoisting machine 3 is released.

As described above, the brake lining 17 generates a loud collision sound by colliding with the brake drum 7 at a high speed by this braking operation. Further, the movable iron core 14 collides with the fixed iron core 11 at a high speed by the braking releasing operation, thereby generating a loud collision sound. Thus, in the hoisting machine brake device 4, a collision sound is generated regardless of the direction of operation. This collision sound propagates through the hoistway and easily leaks into the residential area, which may lead to noise problems for residents, discomfort to passengers, and anxiety. For this reason, the brake device 4 of the hoisting machine is strongly required to be quiet during operation. Furthermore, since it is a device that is used over a long period of time as a feature of this type of device, it is strongly demanded that the silence can be maintained over a long period of time.

A configuration capable of reducing the collision noise of the brake device 4 and extending the life thereof will be described with reference to FIGS. 4A, 4B, 5, 6, and 7. FIG. In FIG. 5, the damping mechanism according to the present invention is exaggerated for easy understanding.

As shown in FIG. 4A, the fixed iron core 11 is formed in the shape of a flat quadrangular prism that is rectangular when viewed from above. Inside the fixed iron core 11, an electromagnetic coil 12 for generating a magnetic force is formed in an elliptical shape, and two braking springs 13 are arranged inside the electromagnetic coil 12. Guide bolts 15 functioning as guide members for the movable iron core 14 protruding toward the movable iron core 14 are fixed to the four corners of the fixed iron core 11. A damping mechanism 18 according to the present invention is provided between the guide bolt 15 and the movable iron core 14. The damping mechanism 18 is formed in the movable iron core 14 in accordance with the arrangement position and the number of the guide bolts 15. Hereinafter, one damping mechanism 18 will be described as a representative.

As shown in FIGS. 4B, 5, and 6, the first damping hole 19 </ b> A and the second damping hole 19 </ b> B through which the guide bolt 15 is inserted are formed at the four corners of the movable iron core 14. The attenuation hole 19A is opened toward the fixed iron core 11 side, and the attenuation hole 19B is opened toward the brake shoe 10 side. Between the damping hole 19A and the damping hole 19B, there is formed an inward flange 20 for generating a reaction force that is formed integrally with the movable iron core 14 and is smaller than the diameter of the damping hole 19A and the damping hole 19B. The inner periphery of the inward flange 20 has a function of adjusting the compression amount of a speed damping elastic body, which will be described later. In the present embodiment, the collar 21 is screwed into the guide bolt 15 and is movable relative to the movable iron core 14.

Inside the damping hole 19A, a first damping rubber 22A having an annular cross-section is disposed as a speed damping elastic body (hereinafter referred to as damping rubber) 22, and similarly, the damping hole 19B has a speed damping elasticity. As a body (hereinafter referred to as a damping rubber) 22, a second damping rubber 22 </ b> B whose annular cross section is rectangular is disposed. Further, a first washer 23A, which is a first load transmission member, is disposed between the damping rubber 22A disposed in the damping hole 19A and the fixed iron core 11, and is similarly fixed to the damping rubber 22B disposed in the damping hole 19B. Between the nuts 16, a second washer 23B, which is a second load transmission member, is disposed. The fixing nut 16 functions as a regulating member that regulates the stop position of the washer 23B.

The diameters of these washers 23A and 23B are smaller than the diameters of the damping holes 19A and 19B. Preferably, the damping rubbers 22A and 22B are covered when the damping rubbers 22A and 22B described later are fully compressed. It is good to be decided to such a diameter.

The diameters of the damping rubber 22A and the damping rubber 22B are determined to be characteristic values in order to suppress the above-described collision noise. That is, between the inward flange 20 and the washers 23A and 23B, when the load is not applied to the damping rubber 22A and the damping rubber 22B, or when the load is less than a predetermined value, the compression is achieved. In the case of deformation, the damping rubber 22A and the damping rubber 22B are determined to have diameters that do not contact the inner peripheral wall surfaces of the damping hole 19A and the damping hole 19B. Conversely, when a load greater than a predetermined value is applied to the damping rubber 22A and the damping rubber 22B, the damping rubber 22A and the damping rubber 22B are compressed between the inward flange 20 and the washers 23A and 23B. Deforms and contacts the inner peripheral wall surfaces of the damping hole 19A and the damping hole 19B to generate a pressing force and a frictional force. The pressing force and the frictional force increase as the load acting on the damping rubber 22A and the damping rubber 22B increases. It is like that.

That is, the maximum load acts on the damping rubber 22A and the damping rubber 22B when the movable iron core 14 is attracted to the fixed iron core 11 and when the movable iron core 14 is separated from the fixed iron core 11 by the braking spring 13. The maximum deformation state. Accordingly, a large pressing force and frictional force are generated between the damping hole 19A and the damping hole 19B formed in the movable iron core 14 and the damping rubber 22A and the damping rubber 22B. On the other hand, while the movable iron core 14 is moving, no load is applied to the damping rubber 22A and the damping rubber 22B between the inward flange 20 and the washers 23A, 23B, or only a load below a predetermined value is acting. Since there is no state, the damping rubber 22A and the damping rubber 22B are not in contact with the inner peripheral wall surfaces of the damping hole 19A and the damping hole 10B.

The operation of the brake device 4 having the damping mechanism 18 having the above-described configuration will be described. When braking the hoisting machine 3 by the brake device 4, electric power supplied to the electromagnetic coil 12 from a controller (not shown). Is interrupted, the movable iron core 14 moves away from the fixed iron core 11 by the elastic force of the brake spring 13, and the brake shoe 10 moves accordingly. At this time, the damping rubber 22A is not deformed in the compression direction because no load is applied between the inward flange 20 and the washer 23A, and the damping rubber 22A does not slide (contact) with the inner peripheral wall surface of the damping hole 19A. Absent.

On the other hand, since the washer 23B is restricted in movement by the fixing nut 16, the damping rubber 22B is compressed as the movable iron core 14 moves between the inward flange 20 and the washer 23B (downward in the drawing). As the amount increases, the damping rubber 22B expands in the circumferential direction, and the pressing force and the frictional force increase due to an increase in the pressing load and an increase in the contact area. For this reason, the damping rubber 22B starts to contact the inner peripheral wall surface of the damping hole 19B in the middle of the movement of the movable iron core 14, and increases its pressing force and friction force as it approaches the maximum movement position. Therefore, the increase in the moving speed of the movable iron core 14 is suppressed by the frictional force of the damping rubber 22B and the elastic force of the damping rubber 22B due to compression. As a result, the speed at which the brake lining 17 of the brake shoe 10 collides with the brake drum 7 is reduced. In addition, since the pressing force is applied, the action of stopping the vibration of the collision sound is strengthened and the collision sound can be reduced.

Next, when releasing the braking of the hoisting machine 3 by the brake device 4, if electric power is supplied to the electromagnetic coil 12 from a controller (not shown) as shown in FIG. 3B, it can move against the elastic force of the braking spring 13. The iron core 14 moves so as to be attracted to the fixed iron core 11, and the brake shoe 10 moves accordingly. At this time, the damping rubber 22B is not deformed in the compression direction because no load is applied between the inward flange 20 and the washer 23B, and the damping rubber 22B does not slide (contact) with the inner peripheral wall surface of the damping hole 19B. Absent.

On the other hand, since the washer 23A is restricted in movement by the fixed iron core 11, the amount of compression of the damping rubber 22A increases between the inward flange 20 and the washer 23A as the movable iron core 14 moves (in the upward direction in the drawing). The damping rubber 22A expands in the circumferential direction, and the pressing force and the frictional force increase due to an increase in the pressing load and an increase in the contact area. For this reason, the damping rubber 22A starts to contact the inner peripheral wall surface of the damping hole 19A in the middle of the movement of the movable iron core 14, and increases its pressing force and friction force as it approaches the maximum movement position. Therefore, the increase in the moving speed of the movable core 14 is suppressed by the frictional force of the damping rubber 22A and the elastic force of the damping rubber 22B due to compression. As a result, the speed at which the movable core 14 collides with the fixed core 11 can be reduced. Moreover, since the pressing force is applied, the action of stopping the vibration of the collision sound is strengthened, and the collision sound can be reduced.

The noise of the brake device 4 of the hoisting machine is a collision sound when the brake lining 17 connected to the movable iron core 14 collides with the brake drum 7 and a collision sound when the movable iron core 14 collides with the fixed iron core 11. For this reason, it is important to reduce the collision speed of the movable iron core 14 and to reduce the vibration after the collision. According to the present embodiment, the speed of the movable iron core 14 is reduced by the frictional force of the damping rubbers 22A and 22B and the elastic force due to the compression, and the damping rubbers 22A and 22B maintain the compressed state even after the collision, and the pressing force is applied to the movable iron core. In order to continue the application, the vibration of the movable iron core 14 can be suppressed.

In the present embodiment, the damping rubbers 22A and 22B do not slide (contact) with the inner peripheral wall surfaces of the damping holes 19A and 19B from the start of the movement of the movable iron core 14 until the predetermined moving amount is reached. The wear and deterioration of 22B can be reduced. As a result, the life of the damping rubbers 22A and 22B can be kept long, and the quietness can be maintained for a long time.

Here, a method for adjusting the initial compression amount of the damping rubbers 19A and 19B will be described. First, the guide bolt 15 is screwed into the screw hole of the guide bolt 15 formed in the fixed iron core 11. Next, a washer 23A and a damping rubber 22A are inserted on the shaft of the guide bolt 15 protruding from the fixed iron core 11, and the movable iron core 14 is connected to the guide bolt 15 via a collar 21 fixed to the inward flange 20 of the movable iron core 14. After that, the damping rubber 22B, the washer 23B, and the fixing nut 16 are inserted and arranged in this order. In this state, the length to the washer 23B and the collar 21 can be adjusted by tightening the fixing nut 16. At this time, the length between the washer 23 </ b> A and the collar 21 can be adjusted by cutting the collar 21 with respect to the inward flange 20 so that the position can be adjusted. Thereby, since the initial compression amount can be adjusted by changing the height of the collar 21, the adjustment becomes simple.

As described above, the outer diameters of the damping rubbers 22A and 22B are smaller than the hole diameters of the damping holes 19A and 19B formed in the movable iron core 8.

A method for adjusting the compression amount of the damping rubbers 22A and 22B and the relationship between the outer diameter Rg of the damping rubbers 22A and 22B and the hole diameter R of the damping holes 19A and 19B will be described with reference to FIGS. The compression amount H that can be compressed by the damping rubbers 22A and 22B is expressed by the equation (1).
H = (hg1 + hg2 + ha1-hc) / 2 (1)
Here, hg1 and hg2 are the heights of the damping rubbers 22A and 22B, ha1 is the height of the inward flange 20, and hc is the height of the collar 21.

In addition, when the damping rubbers 22A and 22B are always in contact with the inner peripheral wall surfaces of the damping holes 19A and 19B, when the movable iron core 14 is moved, wear may occur due to slippage of the moving amount and the life may be shortened. is there. In order to prevent this, when the movable iron core 14 moves, the damping rubber 22A, 22B is compressed, and when it reaches a position where the moving speed of the movable iron core 14 can be reduced against the lateral expansion, the damping rubber 22A. It is important to set the hole diameter R of the attenuation holes 19A and 19B and the outer diameter Rg of the attenuation rubbers 22A and 22B so that the contact holes 22B come into contact with the attenuation holes 19A and 19B.

And the increment Δr of the outer diameter of the damping rubbers 22A and 22B at the time of compression is expressed by the equation (2).
Δr = ν · H / hg (2)
Here, ν is Poisson's ratio (generally about 0.5 for rubber), H is the compression amount of the damping rubbers 22A and 22AB, and hg is the height hg1 or hg2 of the corresponding damping rubbers 22A and 22B.

Accordingly, if the hole diameter R of the damping holes 19A and 19B is in a relationship of Rg <R <Rg + Δr, the damping rubbers 22A and 22B come into contact with the inner peripheral wall surfaces of the damping holes 19A and 19B while the movable iron core 14 is moving. It will be.

As described above, according to the present embodiment, the impact noise can be reduced by reducing the speed of the movable iron core 14 by the frictional force of the damping rubbers 22A and 22B and the elastic force of the damping rubbers 22A and 22B generated by the compression. Even after the collision, the damping rubbers 22A and 22B can suppress the vibration of the movable iron core 14 in order to maintain the compressed state. Further, since the damping rubbers 22A and 22B do not slide (contact) with the inner peripheral wall surfaces of the damping holes 19A and 19B from the start of the movement of the movable iron core 14 until the predetermined moving amount is reached, the wear or deterioration of the damping rubbers 22A and 22B occurs. As a result, the life of the damping rubbers 22A and 22B can be extended and the pressing force can be continuously applied to the movable iron core, and the quietness can be maintained for a long time.

In the hoisting machine brake device 4, the noise is a collision sound when the movable iron core 1 collides with the fixed iron core 11 and a collision sound when the brake shoe 10 collides with the brake drum 7. It is important to reduce the speed and vibration after a collision. It is also important to extend the life of the damping mechanism that reduces the collision speed, particularly the damping rubber that is the main component.

From this point of view, in the damping mechanism 18 proposed in the present embodiment, the damping function of the damping rubbers 22A and 22B is exhibited during the movement of the movable iron core 14, thereby reducing the operating speed of the movable iron core 9 and causing the collision sound. Further, the vibration of the movable core 14 can be suppressed by keeping the damping rubber 22A and 22B in a compressed state after the collision and continuously applying a pressing force to the movable core. At the same time, since the damping rubbers 22A and 22B come into contact with the inner peripheral wall surfaces of the damping holes 19A and 19B from the middle of movement, the contact distance and contact time between the damping rubbers 22A and 22B and the inner peripheral wall surfaces of the damping holes 19A and 19B are short. Therefore, the life of the damping rubbers 22A and 22B can be extended. Thereby, silence can be maintained over a long period of time.

Here, in this embodiment, as a result of measuring and comparing the collision noise of the conventional brake device, it was confirmed that the collision noise was reduced by 2.2 dB when braking and 4.4 dB when releasing the braking.

In the present embodiment, the same material is used for the damping rubbers 22A and 22B. However, when the effect of reducing the noise differs between when the movable iron core 14 is sucked and when the suction of the movable iron core 1 is stopped, it is adjusted accordingly. A desired noise reduction effect can be obtained by changing the elastic coefficients of the damping rubbers 22A and 22B, their diameters, thicknesses, and the like to appropriate ones. For the same reason, the damping rubbers 22A and 22B can be adapted so that the noise reduction effect appears appropriately by making the cross-sectional shapes different, that is, an elastic body such as rubber has an elastic coefficient depending on the cross-sectional shape. It has a changing nature. For example, in the case of a cylinder, the elastic modulus can be changed by changing the inner diameter, outer diameter, and height of the cylinder. In this embodiment, the damping rubbers 22A and 2B are cylinders having a rectangular cross section. However, the present invention is not limited to this, and the cross section may be circular or elliptical.

Here, in the hoisting machine brake device 4, the movable iron core 14 has a braking release operation by the electromagnetic attraction force of the electromagnetic coil 12 and a force in the opposite direction accompanying the braking operation by the braking spring 13 in the opposite direction. It is working. In particular, when performing the releasing operation, the electromagnetic attractive force for attracting the movable iron core 14 must exceed the force obtained by adding the frictional resistance generated by the sliding of the damping rubber 22A to the repulsive force of the braking spring 13. . Therefore, as described in the problem, when the frictional resistance force due to sliding is generated as described above, it is necessary to increase the electromagnetic attraction force from the normal one. Therefore, the number of turns of the electromagnetic coil 12 can be increased. . However, when the number of turns of the electromagnetic coil 12 is increased, the size of the brake device 4 is increased. Similarly, the braking force of the braking spring 13 must be increased with respect to the frictional resistance generated by the damping rubber 22B. For this purpose, the braking spring 13 must be enlarged, which also increases the physique. It becomes.

Therefore, as shown in FIG. 8, the relationship between the braking force, the quietness, and the physique with respect to the magnitude of the frictional force due to the damping of the damping rubber 22A is shown. As can be seen from FIG. 8, there is a trade-off relationship between the physique, the quietness, and the braking force. Therefore, although the quietness is improved by increasing the frictional force of the damping rubber 22A, it is necessary to increase the number of turns of the electromagnetic coil 12 in order to increase the electromagnetic attractive force. Similarly, although the quietness is improved by increasing the frictional force of the damping rubber 22B, there arises a problem that the physique is increased because the braking spring 13 is increased.

On the other hand, although the physique can be reduced by reducing the frictional force of the damping rubber 22A, the speed of the movable iron core 14 by the damping rubber 22A cannot be suppressed, and the impact sound increases. Similarly, although the physique can be reduced by reducing the frictional force of the damping rubber 22B, the speed of the movable iron core 14 by the damping rubber 22B cannot be suppressed, and the collision noise increases.

Therefore, in the case of the configuration in which the damping rubber 22A is slid from these relationships, it is important to appropriately determine the frictional force. It is important to set the frictional force of the damping rubber 22A from the viewpoint of the acceptable physique and quietness based on the trade-off relationship as shown in FIG. The frictional force of the damping rubber 22A may be determined appropriately according to the specifications of the hoist used.

However, unlike the prior art described in the above-mentioned problem section, the above-described problems are in a state where there is almost no pressing force when the damping rubber 22A is not compressed. Since the occurrence of the noise is suppressed to the minimum, the moving speed of the movable core can be suppressed while suppressing the increase in the force that moves the movable core, and the impact noise can be reduced.

To summarize this embodiment, the elastic body is not compressed to a predetermined position in the moving direction of the movable core, so that the elastic body is compressed by moving from the predetermined position in the moving direction of the movable core without sliding or contacting with the movable core. It was made to slide or contact with the movable iron core. Further, the frictional force and the pressing force due to the sliding are increased as the moving iron core moves.

As a result, the elastic body is compressed as the movable iron core moves, and the operating speed of the movable iron core is reduced, so that the impact noise is reduced. The vibration of the movable iron core can be attenuated by expanding in the direction and contacting the elastic body with the movable iron core. Further, as the elastic body is compressed, the elastic force of the elastic body increases and the action of speed reduction increases, and the pressing force also increases as the elastic body is compressed, so that the action of reducing the impact sound is also increased. Further, since the elastic body does not slide with the movable core until the middle of the movement, the wear and deterioration of the elastic body can be suppressed and the silence can be maintained over a long period of time. .

In this embodiment, the collar 21 and the damping rubbers 22A and 22B may be in contact with each other before being compressed, or may be in contact with each other after being compressed. Even if it is the structure which is contacting, if friction rubber | gum 22A, 22B is a state with almost no pressing force between the collar | collar 21 and damping rubber | gum 22A, 22B in a non-compression state, the frictional resistance accompanying sliding will be small. It is because it becomes possible to do. As the damping rubbers 22A and 22B are compressed, the pressing force increases, so that the frictional force between the collar 21 and the damping rubbers 22A and 22B also increases. It contributes to the reduction of Further, if the structure is in contact after being compressed, there is no frictional force between the collar 21 and the damping rubbers 22A and 22B in the non-compressed state, and the compression slides with the moving iron core 14 and contributes to the reduction of the collision speed. You can do it.

Furthermore, in the present invention, the inner diameters of the damping holes 19A and 19B and the outer diameters of the damping rubbers 22A and 22B, and the inner diameters of the damping rubbers 22A and 22B and the outer diameter of the collar 21 may be substantially the same. Even if the inner walls of the attenuation holes 19A and 19B and the outer periphery of the attenuation rubbers 22A and 22B, and the inner periphery of the attenuation rubbers 22A and 22B and the outer periphery of the collar 21 are in normal contact, the attenuation rubbers 22A and 22B are In an uncompressed state, almost no pressing force is applied to the damping holes 19A and 19B and the collar 21 by the damping rubbers 22A and 22B. In such a state, almost no sliding friction force is generated. Moreover, the movable range of the movable iron core 14 is very small. Therefore, the occurrence of wear of the damping rubbers 22A and 22B due to contact is minimized, and it is not necessary to increase the spring force of the brake spring 13 and the magnetic force of the electromagnetic coil 12. When the damping rubbers 22A and 22B are compressed, the same effect as described in the present embodiment can be obtained.

In this embodiment, the collar 21 is fixed to the guide bolt 15. However, the guide bolt 15 and the collar 21 slide with each other, the collar 21 is fixed to the inward flange 20, and the damping rubbers 22A and 22B are compressed. In this case, the frictional force may not be applied, and the speed may be reduced by the elastic force generated by compressing the damping rubbers 22A and 22B themselves. When configured in this manner, lubricating grease or solid lubricant (such as molybdenum disulfide) may be applied to the inside of the collar 21 as necessary, or the collar 21 itself is made of a material having lubricity. It may be formed.

DESCRIPTION OF SYMBOLS 1 ... Riding car, 2 ... Counterweight, 3 ... Hoisting machine, 4 ... Brake device, 5 ... Main rope, 6 ... Sheave, 7 ... Brake drum, 10 ... Brake shoe, 11 ... Fixed iron core, 12 ... Electromagnetic Coil, 13 ... brake spring, 14 ... movable iron core, 15 ... guide bolt, 16 ... fixing nut, 17 ... brake lining, 18 ... damping mechanism, 19A, 19B ... damping hole, 20 ... inward flange, 21 ... collar, 22A , 22B ... damping rubber, 23A, 23B ... washers.

Claims (6)

1. A brake drum provided in a hoist for raising and lowering a car, a brake shoe for braking the brake drum, a movable iron core for driving the brake shoe, a brake spring for driving the movable iron core, and the movable iron core In a brake device for a hoisting machine comprising a fixed iron core provided with an electromagnetic coil that attracts against the spring force of the braking spring,
   The movable core is provided with a speed damping elastic body that limits the moving speed of the movable core, and the speed damping elastic body is not compressed to a predetermined position in the moving direction of the movable core, and the moving direction of the movable core A brake device for a hoisting machine which is compressed and deformed by movement after exceeding a predetermined position.
2. The hoisting machine brake device according to claim 1,
   At least one attenuation hole is formed in the movable iron core. The attenuation hole is smaller than the diameter of the attenuation hole and is compressed and deformed by applying a predetermined load to press the inner peripheral wall surface of the attenuation hole. A hoisting machine brake device comprising the elastic member for speed damping.
3. The hoisting machine brake device according to claim 2,
   The movable iron core is formed with a first damping hole that opens toward the fixed iron core and a second damping hole that opens toward the brake shoe, and the first damping hole has a diameter of the first damping hole. A first damping rubber for speed damping is provided which is smaller and is compressed and deformed by the action of a predetermined load to press the inner peripheral wall surface of the first damping hole, and the second damping hole has the second damping rubber. A second damping rubber for speed damping that is smaller than the diameter of the damping hole and is compressed and deformed by applying a predetermined load to press the inner peripheral wall surface of the second damping hole is provided. Brake device for hoisting machine.
4. The brake device for a hoisting machine according to claim 3,
   An inward flange formed integrally with the movable iron core is formed between the first damping hole and the second damping hole, and a first load transmission member for transmitting a load to the first damping rubber is A second load transmission member is provided so as to sandwich the first damping rubber with the inward flange, and transmits a load to the second damping rubber, and sandwiches the second damping rubber with the inward flange. The first damping rubber or the second damping rubber is deformed by being compressed and deformed by applying a predetermined load to the first load transmitting member or the second load transmitting member. A hoisting machine brake device that presses an inner peripheral wall surface of the second damping hole.
5. In the hoisting machine brake device according to claim 4,
   A guide member protruding toward the movable iron core is fixed to the fixed iron core, and the first attenuation hole, the second attenuation hole, and the inward flange of the movable iron core are inserted into the guide member, Between the first damping rubber and the fixed iron core, the first load transmission member is disposed so as to pass through the guide member, and between the second damping rubber and a regulating member provided on the distal end side of the guide member. The second load transmission member is disposed so as to pass through the guide member, and is compressed and deformed by applying a predetermined load to the first load transmission member or the second load transmission member, thereby causing the first attenuation. A brake device for a hoisting machine, wherein rubber or the second damping rubber presses an inner peripheral wall surface of the first damping hole or the second damping hole.
6. In the hoisting brake device according to claim 5,
   A hoisting machine brake device, wherein a collar having a predetermined length provided in the guide member is inserted through the inward flange.

Images