JP2010254465A - Braking device of elevator and elevator device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a braking device of an elevator capable of preventing the influence of a reaction force that occurs during braking from being exerted on other equipment while independently setting an elastic body for actuation and an elastic body for braking. <P>SOLUTION: This braking device includes rotatable arms 12 for braking arranged in pair, the elastic body 13 for braking interposed between the arms 12 for braking, rotatable arms 14 for actuation arranged in pair inside the arms 12 for braking, the elastic body 15 for actuation interposed between the arms 14 for actuation and an actuator 16, and braking parts 17 arranged in the ends of the arms 12 for braking and the arms 14 for actuation. Moreover, the braking part includes a braking element 17a moved by a frictional force that occurs when pressed to a guide rail, a slope body 17c for actuation supported by the end of the arm for actuation, a slope body 17e for braking supported by the end of the arm for braking, and an elastic body 18 for returning interposed between the braking element and the slope body for actuation for returning the braking element to a neutral position after braking operation. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an elevator braking device, and more particularly, to an elevator braking device that brakes the lifting body when the lifting speed exceeds a predetermined value using an actuator or when the lifting body travels in an uncontrolled state. About.

  As an actuator that uses an actuator to brake the lifting body, the actuator has an operating force that resists the elastic force, and the power is shut off under a predetermined condition. Some have a brake that decelerates and stops the lifting body. And it is mentioned that the device using such an actuator is applied as a device that brakes the lifting body when the lifting speed exceeds a predetermined value or when the lifting body travels in an uncontrolled state. .

  However, in such a device, in order to stop the elevating body by sliding the brake element against the guide rail by elastic force, it is necessary to set an elastic force above a certain level. In order to keep the brake element loaded with force constantly open, the actuator needs to have an actuating force that resists the elastic force. Therefore, it is necessary to increase the capacity of the actuator, and thus the large size of the device. There has been a problem of incurring cost and installation costs. Further, an actuator having a suction force that resists the elastic force needs to further increase the capacity of the actuator in order to ensure a sufficient gap between the brake and the guide rail.

  Therefore, due to the frictional force when pressed against the guide rail, a wedge-shaped brake element that moves upward when the lifting body moves downward, and moves downward when the lifting body moves, and two slopes that form a V-shaped side surface. And a gripper that sandwiches the brake element between the guide rail and an elastic body for operation that moves the brake element in the direction of the braking position via the connecting rod when the actuator is de-energized, and a slide on the guide rail. The structure in which the elastic member for braking that provides the appropriate braking force by applying the pressing force to the contacting brake element is provided independently enables the elastic force of the elastic member for operation to be reduced, and thus the actuator It is conceivable to reduce the capacity of the battery (for example, see Patent Document 1).

JP 2007-277013 A (paragraph numbers 0029 to 0035, FIG. 5)

  However, the above-described conventional structure has a structure in which an actuator is attached to one end of a connecting rod, and a brake element is attached to the other end. The reaction force when sandwiched between them is that which pushes the lifting body away from the guide rail, and that which pushes the guide rail away from the lifting body, which distorts the lifting body or attaches the guide rail It was not preferable because it was a factor to shift

  In addition, since the movable brake element is installed only on one side, there is a problem that the apparatus becomes large in order to ensure the deflection of the braking elastic body in order to exert the necessary braking force. Furthermore, it is conceivable that the elastic body for braking has a high spring constant, the amount of deflection is small, and the necessary braking force is ensured, but in this case, a slight change in the amount of deflection greatly affects the braking force. Therefore, it was necessary to strictly control the dimensions of each part.

  The present invention has been made from the state of the prior art described above, and its purpose is to make the elastic body for operation and the elastic body for braking independent of each other, and the reaction force generated during braking affects other devices. An object of the present invention is to provide a braking device for an elevator that can prevent this and that can be reduced in size and cost when exhibiting the necessary braking force.

  In order to achieve the above object, the present invention provides an elevator braking device provided on a lifting body guided by a guide rail, which is arranged in pairs so as to face each other and rotates via a shaft. A braking arm provided in a possible manner and a braking elastic body interposed between the braking arms are arranged in pairs so as to face each other, and are provided to be rotatable via a shaft. An operating arm; an operating elastic body and an actuator interposed between the operating arms; and the braking arm and a braking portion disposed at an end of the operating arm, and the braking Two slopes are formed on the anti-braking surface to form a V-shaped side surface, and the frictional force when pressed against the guide rail moves upward when the lifting body moves downward. A braking element that is supported by a pair of braking elements that move downward when moved, and an end part of the operating arm, and is formed with two inclined surfaces that are substantially parallel to the inclined surfaces of the braking element, the braking element A braking slope body that is supported by the end of the arm and has two slopes that are substantially parallel to the slopes of the brake element, and is interposed between the brake element and the actuation slope body. Further, it is characterized by having a return elastic body for returning the brake element to the neutral position after the braking operation.

  In the present invention configured as described above, when the actuator is energized, the operating slope body moves in the direction of the guide rail by the elastic force of the operating elastic body interposed between the operating arms. The brake element in which two inclined surfaces are formed so as to form a V-shaped side surface on the anti-braking surface by the frictional force at this time is pressed against the guide rail. Along the slope and the slope of the braking slope body, it moves upward when the lifting body moves downward, and moves downward when it moves upward. In this state, the brake element is pressed against the guide rail with an appropriate pressing force by the elastic force of the braking elastic body interposed between the braking arms via the braking slope body to obtain the braking force. After that, when the lifting and lowering body is operated in the opposite direction to the abnormal operation by the returning operation, the braking element is separated from the guide rail by the elastic force of the returning elastic body interposed between the braking element and the operating slope body. Move in the direction of separation and return to the neutral position.

  Thus, the reaction force when the brake element is pressed against the guide rail turns the pair of braking arms, and this reaction force is caused by the braking elastic body interposed between the braking arms. Since it is absorbed, the reaction force generated during braking does not affect other devices. Further, by providing a structure in which the elastic body for braking and the elastic body for operation are provided independently, it is possible to reduce the elastic force of the elastic body for operation, and thus to reduce the capacity of the actuator. it can.

  According to the present invention, it is possible to prevent the reaction force generated during braking from affecting other devices while reducing the capacity of the actuator. As a result, the apparatus can be reduced in size and cost, and the elevator apparatus can be kept highly accurate and highly reliable. In addition, after the braking operation, the brake can be surely returned to the neutral position, so that a smooth transition to the normal operation can be realized.

It is a schematic block diagram of the elevator which shows the position where the braking device of this invention is installed. 1 is a schematic top view showing an embodiment of an elevator braking device according to the present invention. It is a schematic front view of the braking device in this embodiment. It is a schematic front view which shows a state when the electric current to an actuator is interrupted | blocked. It is a schematic top view which shows a state when the electric current to an actuator is interrupted | blocked. It is a schematic front view which shows a state when the brake is pressing the guide rail at the time of abnormally descending movement. It is a schematic top view which shows a state when pressing the brake element on a guide rail. It is a schematic front view which shows a state when the brake is pressing the guide rail at the time of abnormally rising movement.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of an elevator braking device according to the present invention will be described below with reference to the drawings.

  As shown in FIG. 1, the elevator has a rope 3 wound around a sheave 2 of a hoisting machine provided in a machine room 1, and a counterweight 4 and a counterweight 5 are respectively connected to both ends of the rope 3. ing. The car 4 is guided by a car-side guide rail 7 in the hoistway 6, and the counterweight 5 is guided by the counterweight-side guide rail 8, and the sheave 2 of the hoisting machine is rotated. The car 4 and the counterweight 5 move up and down in the hoistway 6. And the braking device 10 of this embodiment is fastened and fixed to the upper part of the car 4 with a bolt (not shown).

  As shown in FIGS. 2 and 3, the braking device 10 of the present embodiment is disposed in pairs so as to face each other, and is provided with a braking arm 12 that is rotatably provided via a shaft 11. The brake elastic body 13 interposed between the brake arms 12 and the brake elastic body 13 are disposed inside the brake arm 12 so as to be opposed to each other and can be rotated via the shaft 11. , An operating elastic body 15 and an actuator 16 interposed between the operating arms 14, and a braking unit 17 disposed at the ends of the braking arm 12 and the operating arm 14. And.

  The braking portion 17 is formed with two inclined surfaces 17a1 and 17a2 so as to form a V-shaped side surface on the anti-braking surface, and the car 4 is lowered by the frictional force when pressed against the car-side guide rail 7. A pair of brake elements 17a that move upward during movement and a pair of brake elements 17a that move downward during upward movement are rotatably supported on the end of the operating arm 14 via a shaft 17b, and each inclined surface 17a1 of the brake element 17a. , 17a2 and the inclined surface 17c for operation in which the two inclined surfaces 17c1 and 17c2 are substantially parallel to each other, and the end of the braking arm 12 is rotatably supported via the shaft 17d. Two slopes 1 having a cross-sectional shape and having a brake element 17a and an actuating slope body 17c disposed therein and substantially parallel to the slopes 17a1, 17a2 of the brake element 17a. Reference numerals e1 and 17e2 are respectively interposed between the braking slope body 17e formed at the open end and the braking body 17a and the operating slope body 17c. After the braking operation, the braking body 17a is returned to the neutral position. And a return elastic body 18. The return elastic body 18 has one end connected to a support pin 19a provided on the brake element 17a and the other end connected to a support pin 19b provided on the operating slope body 17c to operate with the brake element 17a. It has a structure interposed between the slopes 17c for use.

  In the first embodiment, during normal operation, the actuator 16 is energized to overcome the elastic force of the operating elastic body 15 and separate the brake 17a from the car-side guide rail 7 as shown in FIGS. Is held in the state. At this time, as shown in FIG. 3, each of the slopes 17a1 and 17a2 of the brake element 17a is opposed to the slopes 17c1 and 17c2 of the actuating slope body 17c, and a part of the upper surface and the lower surface of the brake 17a are U-shaped. Is held at a predetermined position by hanging on the inner wall of the braking slope body 17e having a cross-sectional shape. Further, the return elastic body 18 is in a compressed state between the brake element 17a and the operating slope body 17c.

  For example, when a speed detector (not shown) senses an abnormal downward movement of the car 4, an electrical signal is input from the speed detector to the braking device 10, and the braking device 10 interrupts the current to the actuator 16. As shown in FIGS. 4 and 5, the actuator arm 14 is rotated via the shaft 11 by the elastic force of the actuator elastic body 15 interposed between the actuator arms 14, as shown in FIGS. 4 and 5. Then, the operating slope body 17c supported on the end of the operating arm 14 moves in the direction of the car-side guide rail 7, and the brake element 17a is pressed against the car-side guide rail 7.

  At this time, the operating slope body 17c moves in the direction of the car-side guide rail 7, so that the slopes 17c1 and 17c2 of the operating slope body 17c and the slopes 17e1 and 17e2 of the braking slope body 17e are substantially flush with each other. Then, as shown in FIG. 6, when the car 4 is lowered while being pressed against the car-side guide rail 7, the brake element 17a is caused by the frictional force to cause the slope 17c2 of the actuating slope body 17c, and then the braking slope body. It moves upward along the slope 17e2 of 17e. In response to the movement of the brake element 17a, the return elastic body 18 is located between the brake element 17a and the operating slope body 17c and is in an extended state. In this way, when the brake element 17a enters between the car-side guide rail 7 and the inclined surface 17e2 of the braking inclined body 17e, the braking arm 12 rotates through the shaft 11 as shown in FIG. At the same time, the brake 17 a is pressed against the car-side guide rail 7 with an appropriate pressing force by the elastic force of the braking elastic body 13 interposed between the braking arms 12 to brake the car 4.

  When the elevator is returned to normal operation after this braking operation, the actuator 16 is energized to rotate the operating arm 14 in a direction away from the car-side guide rail 7, and the return operation causes the car 4 to malfunction. Drive in the up direction, which is the opposite direction of operation. Correspondingly, the brake element 17a is released from clamping between the car side guide rail 7 and the slope 17e2 of the brake slope body 17e, and is separated from the car side guide rail 7 by the elastic force of the return elastic body 18. And return to the neutral position as shown in FIG.

  On the other hand, when a speed detector (not shown) senses an abnormal upward movement of the car 4, an electrical signal is input from the speed detector to the braking device 10, and the braking device 10 interrupts the current to the actuator 16. As shown in FIGS. 4 and 5, the actuator arm 14 is rotated via the shaft 11 by the elastic force of the actuator elastic body 15 interposed between the actuator arms 14, as shown in FIGS. 4 and 5. Then, the operating slope body 17c supported on the end of the operating arm 14 moves in the direction of the car-side guide rail 7, and the brake element 17a is pressed against the car-side guide rail 7. At this time, the operating slope body 17c moves in the direction of the car-side guide rail 7, so that the slopes 17c1 and 17c2 of the operating slope body 17c and the slopes 17e1 and 17e2 of the braking slope body 17e are substantially flush with each other.

  Then, as shown in FIG. 8, when the car 4 is raised while being pressed against the car-side guide rail 7, the brake element 17a is caused by the frictional force to cause the slope 17c1 of the actuating slope body 17c, and then the braking slope body. It moves downward along the slope 17e1 of 17e. In response to the movement of the brake element 17a, the return elastic body 18 is located between the brake element 17a and the operating slope body 17c and is in an extended state. Thus, when the brake element 17a enters between the car-side guide rail 7 and the inclined surface 17e1 of the braking inclined body 17e, the braking arm 12 rotates via the shaft 11 as shown in FIG. At the same time, the brake 17 a is pressed against the car-side guide rail 7 with an appropriate pressing force by the elastic force of the braking elastic body 13 interposed between the braking arms 12 to brake the car 4.

  When the elevator is returned to normal operation after this braking operation, the actuator 16 is energized to rotate the operating arm 14 in a direction away from the car-side guide rail 7, and the return operation causes the car 4 to malfunction. Drive down, which is the opposite direction of movement. Correspondingly, the brake element 17a is released from clamping between the car side guide rail 7 and the slope 17e1 of the brake slope body 17e, and is separated from the car side guide rail 7 by the elastic force of the return elastic body 18. And return to the neutral position as shown in FIG.

  According to the first embodiment, the reaction force when the brake element 17a is pressed against the car-side guide rail 7 rotates the pair of braking arms 12, and this reaction force is generated between the braking arms 12. Therefore, the reaction force generated during braking does not affect other devices. Further, the structure in which the elastic body for braking 13 and the elastic body for operation 15 are provided independently enables the elastic force of the elastic body for operation 15 to be reduced, and thus the capacity of the actuator 16 is reduced. It can be.

  As a result, the apparatus can be reduced in size and cost, and the elevator apparatus can be kept highly accurate and highly reliable. Further, as described above, the braking device 10 has a structure in which the main portions are paired and provided symmetrically, and the braking arm 12 and the actuation arm 14 rotate via the same shaft 11. Therefore, each part can be operated smoothly, and a pair of brake elements 17a can be uniformly slidably contacted with the guide rail to obtain a stable braking force. Furthermore, the smooth transition to the normal operation can be realized by surely returning the brake element 17a to the neutral position after the braking operation.

DESCRIPTION OF SYMBOLS 1 Machine room 2 Sheave 3 Rope 4 Car 5 Balance weight 6 Hoistway 7 Car side guide rail 8 Balance weight side guide rail 10 Braking device 11 Shaft 12 Braking arm 13 Braking elastic body 14 Acting arm 15 Acting elastic Body 16 Actuator 17 Braking part 17a Braking element 17a1, 17a2 Slope 17b Shaft 17c Slope for operation 17c1, 17c2 Slope 17d Shaft 17e Slope for braking 17e1, 17e2 Slope 18 Restoring elastic body 19a, 19b Support pin

Claims (2)

In the elevator braking device provided on the lifting body guided by the guide rail,
The brake arms are arranged in pairs so as to face each other, and are provided so as to be rotatable via a shaft, and the braking elastic bodies interposed between the brake arms so as to face each other. Are arranged in pairs and are provided so as to be pivotable via a shaft, an elastic body and actuator for operation interposed between these operating arms, the braking arm and the A braking portion disposed at an end of the operating arm, and the braking portion is formed with two inclined surfaces so as to form a V-shaped side surface on the anti-braking surface and pressed against the guide rail. Due to the frictional force at the time, the lifter moves upward when it moves downward, and moves downward when it moves upward, and is supported by the end of the operating arm. flat An actuating slope body in which two slopes are formed, a braking slope body that is supported by an end of the braking arm and has two slopes that are substantially parallel to the respective slopes of the brake element, and An elevator braking apparatus comprising a return elastic body interposed between the brake element and the operating slope body and returning the brake element to a neutral position after a braking operation.   An elevator device comprising the elevator braking device according to claim 1.

Images