JP2016011182A - Governor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact governor capable of setting overspeed being an operation standard of the governor to a different value.SOLUTION: A sheave (101) of a governor (100) of the embodiment comprises a first sheave half body (101a) and a second sheave half body (101b) arranged in a rotation axial line direction of the sheave, and a drive mechanism moves the first and second sheave half bodies relatively in the rotation axial line direction, for changing a gap between the first and second sheave half bodies. By changing the size of the gap, winding radius (R) of a governor rope to the sheave, is changed, and thereby, a ratio of rotation speed of the sheave with respect to movement speed of the governor rope, can be changed.

Description

  Embodiments described herein relate generally to a speed governor that performs a speed control operation by detecting an excess of the traveling speed of an elevator car.

  The elevator is provided with a governor that makes an emergency stop when the car falls into an overspeed state. The governor includes a speed control rope that moves at the same speed as the speed of the car, a sheave around which the speed control rope is wound, and a weight that is displaced by a centrifugal force that changes depending on the rotational speed of the sheave. Have. When the car is in an overspeed state, the actuator mechanically coupled to the weight operates the stop switch, and the power supply of the hoisting machine is shut off. If the speed of the car further increases after the power is cut off (when the car is descending), another operator coupled to the flyweight activates the rope gripping mechanism, thereby operating the emergency stop device. .

  In recent years, for example, in an ultra-high speed elevator or the like, a rated speed when the car is raised is higher than a rated speed when the car is lowered. In this case, the overspeed, which is the speed threshold value for operating the stop switch, is also set to a different value when the car is raised and when the car is lowered. In order to cope with the different overspeeds during ascending and descending times as described above, the speed governor is provided with two detection mechanisms (first detection mechanism and second detection mechanism), which are appropriately combined or selected. To make it work.

  However, when two detection mechanisms are provided in this way, the speed governor becomes large. There is a demand for a speed governor that is more compact and can detect different overspeeds during ascent and descent.

Japanese Patent No. 4306014

  An object of the present invention is to compactly form a speed governor that can set an overspeed as a speed governor operation reference to a different value.

  A speed governor according to an embodiment of the present invention includes a speed control rope that moves in an elevator car, and is connected to a sheave that rotates by movement of the speed control rope, and a rotational speed of the sheave. And a weight that is displaced according to a centrifugal force that changes accordingly, and performs a speed control operation when the amount of displacement of the weight exceeds a predetermined amount due to overspeed of the car. The sheave of this governor has a first sheave half and a second sheave half that are arranged in the direction of the rotational axis of the sheave. A drive mechanism is provided that relatively moves the first and second sheave halves in the direction of the rotation axis and changes the gap between the first and second sheave halves. When the size of the gap between the first and second sheave halves is changed, the wrapping radius of the governor rope on the sheave changes, and the rotational speed of the sheave relative to the speed of movement of the governor rope is changed. The ratio is changed.

It is the whole figure which showed typically the elevator apparatus which can apply the governor provided with the sheave of the division structure concerning one embodiment of the present invention. It is a perspective view which shows an example of the whole structure of the speed governor provided with the sheave of the division structure which concerns on one Embodiment of this invention. It is the schematic for demonstrating one structural example of the speed governor provided with the sheave of the division structure which concerns on one Embodiment of this invention. It is the schematic for demonstrating the other structural example of the speed governor provided with the sheave of the division structure which concerns on one Embodiment of this invention. FIG. 6 is a schematic diagram for explaining the arrangement of belts in the configuration example of FIG. 5. It is a schematic sectional drawing which shows an example of the mechanism which enables the relative movement of the rotational axis direction of sheave half bodies.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

  First, an example (not limited to) an overall configuration of an elevator apparatus to which a governor according to an embodiment of the present invention can be applied will be described with reference to FIG.

  In FIG. 1, reference numeral 1 denotes an elevator hoistway, and reference numeral 2 denotes a machine room provided in the upper part of the hoistway 1. The machine room 2 is provided with a hoisting machine 3 having a driving sheave 3a and a deflecting wheel 4. A hoisting rope (main rope) 5 is wound around the hoisting machine 3 and the deflecting wheel 4. An elevator car 6 is suspended from one end of the hoisting rope 5, and a counterweight 7 is suspended from the other end of the hoisting rope 5. The car 6 and the counterweight 7 are moved up and down in the hoistway 1 in opposite directions by driving the hoisting machine 3.

  At the bottom of the pit of the hoistway 1, there are provided a car buffer 8 and a counterweight buffer 9 that alleviate the impact caused by the collision with the car 6 and the counterweight 7 that are dropped in an emergency.

  In the present embodiment in which a control device 10 for controlling the operation of the hoisting machine 3 is provided in the machine room 2, the car 6 is controlled at different speeds when it is raised and lowered by the control of the controller 10. Driven.

  The car 6 is provided with an emergency stop device 11. An endless speed regulating rope 13 is connected to the emergency stop device 11 via an arm 12 that forms a part of a link mechanism (not shown in detail) called a safety link attached to the car 6. The governing rope 13 is wound around a tension wheel 14 provided at the bottom of the hoistway 1 and a sheave 101 provided on the governor 100 in the machine room 2.

  Since the speed control rope 13 is connected to the car 6 through the link mechanism (having the arm 12) (not shown) described above, the speed control rope 13 follows the up and down of the car 6 during normal operation. 14 and the sheave 101 move in a circulating manner. Accordingly, the rotational speed of the sheave 101 changes corresponding to the speed of the car 6. The speed governor 100 detects that the speed of the car 6 has exceeded a predetermined speed based on the displacement of a flyweight (described later in detail) that is displaced by centrifugal force according to the rotational speed of the sheave 101, and adjusts the speed of the car 6. Do speed.

  The governor 100 detects a predetermined speed when the car 6 is raised (for example, about 1.3 times the rated speed) as the first rising overspeed VU1, and the predetermined speed when the car 6 is lowered is the first descending overspeed. Detect as VD1. When these overspeeds VU1 and VD1 are obtained, the hoisting machine 3 is stopped.

  If the car 6 does not stop even if the driving of the hoisting machine 3 is stopped, the speed governor 100 detects the second descending overspeed VD2 that is faster than the first descending overspeed VD1. When the second descending overspeed VD2 is detected, the speed governor 100 grips and brakes the speed control rope 13 by the rope gripping mechanism 102. Thereby, the speed control rope 13 is pulled up with respect to the cage | basket | car 6, and the emergency stop apparatus 11 operate | moves via the link mechanism not shown including the arm 12. FIG. The emergency stop device 11 holds a guide rail (not shown) with a brake shoe (not shown) and stops the lowering of the car 6.

  As the configuration of the governor 100, a known one can be adopted except that the sheave 101 is divided as described later. An example of the configuration of the governor 100 that can be adopted will be briefly described with reference to FIG.

  The governor 100 is of a flyweight type. The speed governor 100 includes a frame 103 that supports a rotating shaft 101 </ b> A of the sheave 101. A pair of flyweights 104 is attached to the sheave 101. The flyweight 104 is attached to the sheave 101 via a shaft 105 so as to be swingable about a swing axis extending in the horizontal direction. Note that when the sheave 101 is divided into two halves as described later, the flyweight 104 may be attached to one of the halves. The pair of flyweights 104 are connected to each other by a connecting rod 106, and the displacement amount (swinging angle) of both flyways 104 is kept the same.

  The flyweights 104 are subjected to centrifugal force by an urging mechanism 107 for adjusting values (initial values) of overspeeds (the above-described overspeeds VU1, VD1, and VD2) at which the speed control operation is performed. The spring is always biased in the direction opposite to the direction of displacement when received.

  A ratchet wheel 108 coaxial with the sheave 101 is provided adjacent to the sheave 101 in the axial direction. The ratchet wheel 108 is stationary without rotating during normal operation. The ratchet wheel 108 is provided with a holding claw (not visible in FIG. 2) on the outer periphery, and the holding claw holds the rope gripping mechanism 102 in the rope release position (the obliquely inclined position shown in FIG. 2). doing.

  When the displacement (fluctuation angle about the shaft 105) of the flyweight 104 exceeds the first predetermined amount, an operating pin (not shown) attached to the flyweight 104 is moved to the stop switch 109. By touching, the stop switch 109 is operated, and the driving of the hoisting machine 3 is stopped.

  When the displacement due to the centrifugal force of the flyweight 104 exceeds the second predetermined amount, the operating pawl (not visible in FIG. 2) attached to the flyweight 104 meshes with the protrusion of the ratchet wheel 108, and the ratchet wheel 108 Rotate. Thereby, the holding of the rope gripping mechanism 102 by a holding claw (not shown) of the ratchet wheel 108 is released, and the rope gripping mechanism 102 falls down horizontally. As a result, the rope gripping member 102a faces the stationary rope gripping member 102b, and the rope gripping member 13 is pulled by the elastic force of a spring (not visible in FIG. 2) provided on the rope gripping mechanism 102. It presses against 102b, and thereby the speed control rope 13 is braked and the emergency stop device 11 is activated.

  Next, the configuration of the sheave 101 that can change the overspeed to be detected will be described with reference to FIG.

  The sheave 101 is divided into two in the axial direction, that is, the sheave is composed of two sheave halves 101a and 101b. The sheave halves 101a and 101b are relatively movable in the axial direction, and the interval G in the rotational axis direction of the sheave halves 101a and 101b is variable. In the illustrated embodiment, the sheave half 101a is stationary in the direction of the rotational axis, and the sheave half 101b is movable in the direction of the rotational axis. Such relative movement of the sheave halves 101a and 101b can be realized by providing an appropriate hydraulic drive mechanism (an example of which will be described later).

  The sheave halves 101a and 101b have inclined surfaces 101c and 101d that face each other. The governing rope 13 is in contact with the sheave 101 over the almost half of the sheave 101 in the upper half of the sheave 101, and is supported on the inclined surfaces 101c and 101d.

  When the movable sheave half 101b is moved so as to be close to the sheave half 101a from the state shown in FIG. 3B and the distance G between the sheave halves 101a and 101b is narrowed, the tension wheel 14 gives it. Contrary to the applied tension, the speed control rope 13 slides on the inclined surfaces 101c, 101d and moves radially outward, and the winding radius R of the speed control rope 13 around the sheave 101 (the speed control rope 13 is the sheave). (Bending radius of bending following 101) is increased. On the other hand, when the movable sheave half 101b is moved away from the sheave half 101a from the state shown in FIG. The rope 13 slides on the inclined surfaces 101c and 101d and moves inward in the radial direction, and the winding radius R of the speed control rope 13 becomes small.

  When the movement speed of the speed control rope 13 is the same, the rotation speed of the sheave 101 increases as the winding radius R of the speed control rope 13 around the sheave 101 decreases. Therefore, as described above, when the first ascending overspeed VU1 is desired to be larger than the first descending overspeed VD1, when the car 6 is raised, the interval G is narrowed to increase the winding radius R, and when the car 6 is raised. What is necessary is just to enlarge the space | interval G and to make the winding radius R small.

  In order to increase the amount of change of the winding radius R, the inclination angle of the inclined surfaces 101c and 101d is increased (standing) or the movement amount of the movable sheave half 101b is increased. There is a need. However, if the inclination angle of the inclined surfaces 101c and 101d is excessively increased, the speed control rope 13 may be locked between the sheave halves 101a and 101b. Further, the upper limit of the moving amount of the movable sheave half 101 b is restricted by the diameter of the speed control rope 13.

  The above problem can be solved by sandwiching an endless belt 200 between the speed control rope 13 and the sheave 101 as shown in FIG. As shown schematically in FIG. 5, such a belt 200 includes a pulley 202 supported by a support body 201 provided on the lower surface of the bottom wall 2 a of the machine room 2 (the ceiling wall of the hoistway 1), and a sheave. 101. In this case, since the distance between the pulley 202 and the sheave 101 is relatively small, an appropriate belt tensioner or tension adjuster (in order to absorb fluctuations in the tension of the belt 200 accompanying the movement of the movable sheave half 101b) (Not shown) may be provided.

  As shown in FIG. 4, the belt 200 is substantially V-shaped (that is, a V-belt), and the side surface of the belt 200 is inclined at substantially the same angle as the inclined surfaces 101c and 101d. In order to maintain the speed control rope 13 at the center in the width direction of the belt 200, the center portion in the width direction of the outer peripheral surface of the belt 200 is lowered.

  When the movable sheave half 101b is moved closer to the sheave half 101a from the state shown in FIG. 4B to narrow the gap G between the sheave halves 101a and 101b, the belt 200 is inclined. 101c and 101d slide on the outer side in the radial direction, the wrapping radius R of the belt 200 increases, and the speed control rope 13 is pushed by the belt 200 and moves outward in the radial direction. The winding radius R is increased. On the other hand, when the movable sheave half 101b is moved away from the sheave half 101a from the state shown in FIG. 4A to widen the gap G, the belt 200 slips on the inclined surfaces 101c and 101d. The speed adjusting rope 13 moves inward in the radial direction, and the speed adjusting rope 13 also moves inward in the radial direction, and the winding radius R of the speed controlling rope 13 decreases. Therefore, as in the embodiment shown in FIG. 3, it is possible to change the overspeed that is the trigger for the speed control operation.

  In the configuration example shown in FIG. 4, as long as the belt 200 does not fall into the gap between the sheave halves 101a and 101b (actually, a certain safety margin is required), the sheave halves 101a and 101b The interval G can be increased. That is, by using the belt 200 having a width wider than the diameter of the speed control rope 13, compared with the case where the belt 200 is not used, the adjustment width of the gap G, that is, the winding of the speed control rope 13 around the sheave 100. The adjustment range of the radius R can be increased. That is, it is possible to widen the overspeed adjustment range that serves as a reference for starting the speed control operation of the speed governor 100.

  As a hydraulic drive mechanism that enables relative movement of the sheave halves 101a and 101b, for example, the principle of a rotating hydraulic cylinder used in a machine tool or a pulley (disc) of a continuously variable transmission (CVT) used in an automobile The thing using the principle of a moving mechanism can be used.

  A configuration example of a hydraulic drive mechanism using the principle of a rotating hydraulic cylinder will be briefly described below with reference to FIG. FIG. 6 is a schematic diagram, and even if a part formed by joining a plurality of parts, if the combined body moves together, they are continuously displayed as one part with the same hatching. In FIG. 6, a member indicated by a square box with a cross marked therein is a roller bearing, and a member indicated by a black circle is an oil seal.

  One end of the rotating shaft 301 of the movable sheave half 101 b is supported on the right portion 103 a of the frame 103 via a hollow shaft support 302. The shaft support 302 itself can freely rotate, and the rotation shaft 301 can slide in the axial direction within the shaft support 302. A piston 303 is provided on the rotating shaft 301. The piston 303 is accommodated in a cylinder 305 formed in a rotating component 304 that rotates integrally with the sheave half 101a that does not move in the axial direction. The rotation shaft 301 is inserted into the inside of the cavity at the center of the rotation component 304, and the rotation shaft 301 is slidable with respect to the rotation component 304. Further, the rotation shaft 301 and the rotation component 304 are not allowed to rotate relative to each other by the rotation prevention pin 310. Instead of providing the anti-rotation pin 310, the rotating shaft 301 and the rotating component 304 may be coupled via a spline or serration so that they cannot be rotated relative to each other and can move in the direction of the relative rotating axis. The rotating component 304 is supported by the left portion 103b of the frame 103 so as to be rotatable and not movable in the axial direction. An oil supply groove 306 is formed over the entire circumference of the outer periphery of the rotating component 304, and pressure oil is supplied to the oil supply groove 306 from an oil supply port 307 provided in a component coupled to the frame 103. The pressure oil is supplied into the cylinder chamber 309 through an oil passage 308 in the rotating component 304 communicating with the oil supply groove 306, whereby the piston 303 and the movable sheave half 101b coupled thereto are illustrated. Move to the middle left. The reverse movement of the movable sheave half 101b is realized by the spring force of the return spring 311 provided between the sheave halves 101a and 101b and the tension of the speed control rope 13, and at this time, the inside of the cylinder chamber 309 The pressure oil is returned to an oil sump (not shown) through a return oil path (not shown).

  According to the above embodiment, it is possible to adjust the overspeed that is the reference for the speed control operation by the relative movement of the sheave halves 101a and 101b. If this configuration is adopted, only one speed adjusting mechanism is required. For this reason, the governor which can set the overspeed used as a governor operation reference to a different value can be formed compactly.

  The above embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

13 Control rope 100 Sheave 101a, 101b Sheave half 200 Endless belt

Claims (5)

A speed-control rope that moves with the elevator car is wound around, and a sheave that rotates by the movement of the speed-control rope, and a centrifugal force that is coupled to the sheave and changes according to the rotational speed of the sheave A speed governor that performs a speed control operation when a displacement amount of the weight exceeds a predetermined amount due to overspeed of the car,
The sheave has a first sheave half and a second sheave half aligned in the rotational axis direction of the sheave;
A drive mechanism is provided for moving the first and second sheave halves relative to each other in the rotational axis direction and changing a gap between the first and second sheave halves;
By changing the size of the gap, the radius of wrapping of the speed control rope around the sheave is changed, thereby making it possible to change the ratio of the rotational speed of the sheave to the speed of movement of the speed control rope. Speed governor.   The 1st inclined surface which contact | connects the said speed control rope is provided in the outer peripheral part of the said 1st sheave half body, and the 2nd inclined surface which contact | connects the said speed control rope in the outer peripheral part of the said 2nd sheave half body The speed governor according to claim 1, wherein the first and second inclined surfaces are inclined in opposite directions so that the distance between the first and second inclined surfaces increases toward the outer side in the radial direction. A first inclined surface is provided on an outer peripheral portion of the first sheave, a second inclined surface is provided on an outer peripheral portion of the second sheave, and the first and second inclined surfaces have a radius Inclined in opposite directions so that the distance between them increases as you go outward, facing each other,
The speed governor further includes an endless belt wound between the sheave and a pulley, and the endless belt is sandwiched between the first and second inclined surfaces. Wrapped around
The governor according to claim 1, wherein the governor rope is wound around the sheave via the endless belt while being supported on an outer peripheral surface of the endless belt.   The governor according to claim 3, wherein the endless belt is a V-belt.   5. The speed governor according to claim 3, wherein a center portion in the width direction of the outer peripheral surface of the endless belt is recessed in order to position the speed control rope at a center portion in the width direction of the outer peripheral surface of the endless belt.

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