WO2006038300A1

WO2006038300A1 - Elevator apparatus

Info

Publication number: WO2006038300A1
Application number: PCT/JP2004/014834
Authority: WO
Inventors: Eiji Ando
Original assignee: Mitsubishi Denki Kabushiki Kaisha
Priority date: 2004-10-07
Filing date: 2004-10-07
Publication date: 2006-04-13
Also published as: JPWO2006038300A1; CN100569619C; CN1902118A; EP1798183A4; EP1798183B1; EP1798183A1

Abstract

Supported on a base is a governor rope pulley which is rotatable integrally with a rope pulley shaft. The governor rope pulley is provided with a flyweight which is displaced from the normal position to a trip position by the centrifugal force due to the rotation of the governor rope pulley. The rope pulley shaft is provided with an adjusting lever turnable peripherally of the governor rope pulley. Connected between the flyweight and the adjusting lever is a connector having a balance spring urging the flyweight in a direction counter to the centrifugal force. The rope pulley shaft is provided with an operating member capable of being displaced axially of the rope pulley shaft. The adjusting lever is made turnable by the displacement of the operating member axially of the rope pulley shaft. Therefore, the adjustment of the distance of the normal position with respect to the trip position is made by the turning of the adjusting lever.

Description

Specification

Elevator equipment

Technical field

The present invention relates to a speed governor for an elevator having a speed governor sheave that is rotated as a force moves.

Background art

[0002] In a conventional elevator governor, a flyweight provided on the governor sheave rotates the governor sheave to detect that the speed of the force has reached a predetermined overspeed. It may be rotated by centrifugal force. The cage is equipped with an emergency stop device to prevent the force from falling. The governor sheave is wrapped around a governor rope connected to an emergency stop device. Therefore, the governor sheave is rotated at a speed corresponding to the speed of the force.

[0003] In this conventional elevator governor, when the rotational speed of the governor sheave reaches the first overspeed, the car stop switch is activated by the rotation of the flyweight. The operation of the force stop switch cuts off the power to the elevator drive unit and the car is stopped by the brake unit of the drive unit. In addition, when the speed of the governor sheave reaches the second overspeed, the flyweight is further rotated, and the braking mechanism for braking the governor rope is operated. The governor rope is braked by the operation of the braking mechanism, and the emergency stop device is operated by the braking of the governor rope (see Patent Document 1).

[0004] Patent Document 1: Japanese Patent Laid-Open No. 2001-106454

Disclosure of the invention

Problems to be solved by the invention

However, in such a conventional elevator governor, the settings of the first and second overspeeds cannot be adjusted during operation of the elevator. Therefore, the overspeed set for the governor is constant regardless of the position of the car. This prevents the governor from operating until the car speed is extremely high, even when the car is moving up and down the hoistway where the car speed is usually low. . Therefore, the impact on the force The size of the shock absorber for buffering cannot be reduced, and the depth of the pit portion of the hoistway where the shock absorber is installed cannot be reduced. In addition, the overhead size for allowing excessive force and jumping increases, and the overhead size cannot be reduced.

[0006] The present invention has been made to solve the above-described problems, and provides an elevator governor capable of easily adjusting a set overspeed for emergency stop of a car. For the purpose.

Means for solving the problem

[0007] An elevator governor according to the present invention includes a sheave shaft that is rotatably supported on a base, a governor rope that moves together with a force, and a speed governor that can rotate integrally with the sheave shaft. It can be displaced with respect to the governor sheave between the normal position and the trip position that is located radially outside the governor sheave. A flyweight that is displaced from the normal position to the trip position by the centrifugal force caused by the rotation of the governor sheave, a braking mechanism that is actuated by the displacement of the flyweight to the trip position and applies braking force to the governor rope, and the rope An adjustment lever that can rotate in the circumferential direction of the governor sheave relative to the axle, and a balance spring that biases the flyweight in a direction against the centrifugal force caused by the rotation of the governor sheave. Linked body, sheave connected between levers Provided with an operating member that can be displaced in the axial direction of the sheave shaft, and an interlocking mechanism that interlocks the operating member and the adjusting lever with each other. The adjusting lever is provided by the displacement of the operating member in the axial direction of the sheave shaft. The distance can be adjusted with respect to the trip position of the normal position by rotating the adjustment lever.

Brief Description of Drawings

FIG. 1 is a configuration diagram showing an elevator apparatus according to Embodiment 1 of the present invention.

FIG. 2 is a front view showing the governor of FIG.

FIG. 3 is a rear view showing the governor of FIG. 2.

[4] FIG. 4 is a partial cross-sectional view showing a main part of the governor of FIG.

FIG. 5 is an exploded perspective view showing a main part of the governor of FIG.

[Fig. 6] The car speed, first overspeed and second overspeed during normal operation of the elevator of Fig. 1 The lowest floor force is a graph showing the relationship with the distance to the car.

FIG. 7 is a cross-sectional view of an essential part showing an elevator governor according to Embodiment 2 of the present invention.

FIG. 8 is a main part configuration diagram showing the governor as viewed along the radial direction of the governor sheave in FIG.

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.

Embodiment 1.

FIG. 1 is a configuration diagram showing an elevator apparatus according to Embodiment 1 of the present invention. In the figure, a driving device 2 is installed in the upper part of the hoistway 1. A main rope 3 is wound around a sheave 2 a of the driving device 2. In the hoistway 1, a car 4 and a counterweight 5 are suspended by a main cable 3. In addition, in the hoistway 1, a pair of force guide rails 6 for guiding the raising and lowering of the car 4 and a pair of counterweight guide rails (not shown) for guiding the raising and lowering of the counterweight 5 are installed. It has been.

[0010] An emergency stop device 7 for preventing the force cage 4 from dropping is provided below the cage 4. A governor support member 8 is fixed to the upper portion of the car guide rail 6. On the governor support member 8, a governor 9 that detects an overspeed of the car 4 and operates the emergency stop device 7 is supported.

In the vicinity of the bottom of the hoistway 1, a rotatable tensioning wheel 10 is provided. A governor rope 11 is wound around the governor 9 and the tension wheel 10. One end and the other end of the governor rope 11 are connected to the emergency stop device 7 via a lever 12. The governor rope 11 is circulated as the force 4 moves up and down.

FIG. 2 is a front view showing the governor 9 of FIG. In the figure, a base 13 is fixed on the governor support member 8. A horizontally extending sheave shaft 14 is rotatably supported on the base 13. A speed governor sheave 15 around which a speed governor rope 11 is wound is fixed on the sheave wheel shaft 14. The governor sheave 15 is rotated integrally with the sheave shaft 14.

On the side surface of the governor sheave 15, a pair of flyweights 17 that can rotate around a pin 16 is provided. Each flyweight 17 can be displaced between a normal position and a trip position positioned radially outward of the governor sheave 15 with respect to the normal position by rotating around the pin 16. It is functioning. Each flyweight 17 is rotated from the normal position to the trip position by the centrifugal force generated by the rotation of the governor sheave 15. The flyweights 17 are connected to each other by links 18.

An operating claw 19 is fixed to one end portion of one flyweight 17. The operating claw 19 is displaced outward in the radial direction of the governor sheave 15 by the rotation of the flyweight 17 from the normal position to the trip position.

[0015] A car stop switch 20 for stopping power supply to the drive device 2 and operating a brake device (not shown) of the drive device 2 is attached to the base 13. The car stop switch 20 includes a switch body 21 and a switch lever 22 provided on the switch body 21 and operated by an operating claw 19. The switch lever 22 is operated by the operating claw 19 when the flyweight 17 is rotated to the stop operation position located between the normal position and the trip position. The flyweight 17 is rotated to the stop position when the speed of the force 4 reaches the first overspeed (usually about 1.3 times the rated speed), and the speed of the car 4 becomes the second speed. When the overspeed (usually about 1.4 times the rated speed) is reached, the trip position is turned.

The governor sheave 15 is provided with a trip lever 24 that is rotatable about an axis 23 that is parallel to the pin 16. A part of the trip lever 24 is in contact with one flyweight 17. The trip lever 24 is rotated about the shaft 23 by the rotation of the flyweight 17. The shaft 23 is provided with a twisting spring (not shown) that urges the trip lever 24 in a direction to contact the flyweight 17.

[0017] The base 13 is provided with a ratchet 25 that can rotate around the sheave axle 14. The ratchet 25 is rotated with respect to the sheave axle 14. A plurality of teeth are provided on the outer periphery of the ratchet 25.

One pin 16 is rotatably provided with an engaging claw 26 that selectively engages one of the trip lever 24 and the ratchet 25. The engaging claw 26 is urged in a direction to engage with the ratchet 25 by a pulling spring (not shown). The engaging claw 26 is engaged with the trip lever 24 and separated from the ratchet 25 when the flyweight 17 is in the normal position. Further, when the flyweight 17 is rotated to the trip position, the engaging claw 26 is disengaged from the trip lever 24 and is rotated by the spring force of the pulling spring to engage the ratchet 25. Match.

In addition, an arm 27 is rotatably attached to the base 13. The arm 27 is rotatably attached with a shoe 28 that is pressed against the governor sheave 15 via the governor rope 11. A spring shaft 29 is displaceably passed through the tip 27a of the arm 27. A connection link 30 that is rotatably connected to the ratchet 25 is fixed to one end of the spring shaft 29. A spring receiving member 31 is provided at the other end of the spring shaft 29. A pressing spring 32 for pressing the shoe 28 against the governor rope 11 is provided between the tip 27 a of the arm 27 and the spring receiving member 31.

The ratchet 25 is rotated in the same direction as the governor sheave 15 by engagement with the engaging claw 26 when the governor sheave 15 is rotated. As a result, the arm 27 is rotated in a direction in which the shoe 28 is pressed against the governor sheave 15. The movement of the governor rope 11 is braked by pressing the shush 28 against the governor sheave 15 through the governor port 11.

[0021] The braking mechanism 33 for applying a braking force to the governor rope 11 includes a trip lever 24, a ratchet rod 25, an engagement claw 26, an arm 27, a shear 28, a spring shaft 29, a connection link 30, and a spring. A receiving member 31 and a pressing spring 32 are provided.

FIG. 3 is a rear view showing the governor 9 of FIG. In the figure, the sheave shaft 14 is provided with an adjustment lever 34 that can rotate in the circumferential direction of the governor sheave 15 with respect to the sheave shaft 14. The adjustment lever 34 is provided with a lever body 35 including a cylindrical portion 35a through which the sheave shaft 14 is passed inward, and an elongated hole 36 that is provided on the outer periphery of the lever body 35 and extends in the circumferential direction of the governor sheave 15. The rotation restricting portion 37 is provided, and a lever piece 38 is provided on the outer peripheral portion of the lever main body 35 and extends radially outward of the lever main body 35.

A pin 39 that is passed through the long hole 36 is fixed to the side surface of the governor sheave 15. The pin 39 can slide in the long hole 36 in the length direction of the long hole 36. The rotation restricting portion 37 is slid with respect to the pin 39 by the rotation of the adjusting lever 34 with respect to the sheave shaft 14. Thereby, the rotation amount of the adjustment lever 34 is regulated.

The lever piece 38 is displaced in the circumferential direction of the governor sheave 15 by the rotation of the lever body 35. A connecting body 40 that connects the flyweight 17 and the adjustment lever 34 is connected between the other end of one flyweight 17 and the lever piece 38. Link 40 is The telescopic rod 41 connected between the flyweight 17 and the lever piece 38 and the telescopic rod 41 are provided on the telescopic rod 41 and urge the flyweight 17 in the direction against the centrifugal force caused by the rotation of the governor sheave 15. And a balance spring 42.

The flyweight 17 and the adjustment lever 34 are interlocked with each other by the connecting body 40. Accordingly, the normal position of the flyweight 17 can be adjusted in the direction toward or away from the trip position by the rotation of the adjustment lever 34. That is, the rotation angle (rotation distance) of the flyweight 17 until it is displaced to the normal position force trip position can be adjusted by the adjustment lever 34. As a result, the magnitudes of the first and second overspeeds for emergency stop of the car 4 can be adjusted by turning the adjustment lever 34.

FIG. 4 is a partial cross-sectional view showing a main part of the governor 9 of FIG. FIG. 5 is an exploded perspective view showing a main part of the governor 9 of FIG. The sheave shaft 14 is provided with an operation member 43 that can be displaced in the axial direction of the sheave shaft 14. The operation member 43 includes a pipe part 44 surrounding the sheave shaft 14 and a plate-like disk part 45 provided on the outer peripheral part of the pipe part 44. The disc part 45 is arranged on the sheave shaft 14 perpendicular to the axis.

An interlocking mechanism 46 that interlocks the operation member 43 and the adjustment lever 34 is provided between the sheave wheel shaft 14 and the lever main body 35. The interlocking mechanism 46 converts the displacement of the operation member 43 relative to the sheave shaft 14 into rotation of the adjustment lever 34 relative to the sheave shaft 14.

[0028] The interlocking mechanism 46 is provided on the outer peripheral surface of the sheave shaft 14 with the displacement body 47 integrated with the operation member 43, and when the displacement body 47 is displaced with respect to the sheave shaft 14, the displacement body 47 Provided on the sheave shaft side spline portion 48, which is the first guide for rotating 47 against the sheave shaft 14 and the inner surface of the cylindrical portion 35a, the displacement body 47 is displaced with respect to the sheave shaft 14. In some cases, a lever-side spline portion 49 that rotates the cylindrical portion 35a with respect to the displacement body 47 in a direction opposite to the rotation direction of the displacement body 47 by the sheave shaft side spline portion 48 is provided.

[0029] An internal spline portion 50 fitted to the sheave shaft side spline portion 48 is provided on the inner peripheral surface of the displacement body 47, and the lever side spline portion 49 is fitted to the outer peripheral surface of the displacement body 47. An external spline portion 51 is provided. In other words, the displacement body 47 is splined to the lever body 35 and the sheave shaft 14. Thereby, the displacement body 47 can be displaced while being rotated in the axial direction of the sheave shaft 14 with respect to the sheave shaft 14 and the cylindrical portion 35a. It has become.

Each tooth of the sheave shaft side spline portion 48 and the lever side spline portion 49 is inclined with respect to the axial direction of the sheave shaft 14. That is, the sheave shaft side spline portion 48 and the lever side spline portion 49 are helical spline portions. Further, the inclination direction (twisting direction) of the tooth trace of the sheave shaft side spline part 48 is opposite to the inclination direction (torsion direction) of the tooth line of the lever side spline part 49. Further, the inclination angle (torsion angle) of the tooth trace of the sheave shaft side spline part 48 is different from the inclination angle (torsion angle) of the tooth line of the lever side spline part 49.

[0031] When the displacement body 47 is displaced in the axial direction of the sheave shaft 14 with respect to the sheave shaft 14, the rotation of the displacement body 47 with respect to the sheave shaft 14 and the rotation of the cylindrical portion 35a with respect to the displacement body 47 are simultaneously performed. Done. The direction of rotation of the displacement body 47 relative to the sheave shaft 14 and the direction of rotation of the cylindrical portion 35a relative to the displacement body 47 are opposite to each other. Therefore, when the displacement body 47 is displaced in the axial direction of the sheave shaft 14, the adjustment lever 34 has an angular difference between the rotation angle of the displacement body 47 with respect to the sheave shaft 14 and the rotation angle of the cylindrical portion 35a with respect to the displacement body. Only the sheave shaft 14 is rotated.

[0032] The base 13 is provided with an actuator device (not shown) for displacing the operation member 43 in the axial direction of the sheave shaft 14. The actuator device has an arm portion that contacts the disk portion 45 and displaces the operation member 43. Further, the sheave shaft 14 is provided with an encoder (not shown) which is a detection unit for detecting the position and speed of the car 4. The encoder generates a signal corresponding to the rotation of the governor sheave 15 and sends the generated signal to an elevator control device (not shown). The elevator control device controls the actuator device based on the information of the elevator!

FIG. 6 is a graph showing the relationship between the speed of the car 4, the first overspeed and the second overspeed, and the distance from the lowest floor to the car 4 during normal operation of the elevator shown in FIG. In the figure, the hoistway 1 has an acceleration / deceleration zone where the car 4 is accelerated / decelerated near the lowermost floor and the uppermost floor (one and the other terminal floor), and the car 4 is constant between each acceleration / deceleration section. There is a constant speed section that moves at a speed of.

[0034] The elevator control device includes a normal speed pattern 55 that is the speed of the car 4 during normal operation. The first overspeed pattern 56, which is greater than the normal speed pattern 55, and the second overspeed pattern 57, which is greater than the first overspeed pattern 56, are at the position of the car 4, respectively. It is set correspondingly.

[0035] The normal speed pattern 55, the first overspeed pattern 56, and the second overspeed pattern 57 are continuously reduced toward the final floor in the acceleration / deceleration section so as to have a constant value in the constant speed section. Each is set.

[0036] The elevator control device controls the actuator device such that the magnitudes of the first and second overspeeds are adjusted along the first and second overspeed patterns 56 and 57, respectively. . In other words, the elevator control device has an actuator device so that each of the first and second overspeeds continuously decreases as the position of the car 4 approaches the lowermost floor or the uppermost floor in the acceleration / deceleration section. To control!

[0037] In this example, when the car 4 is moved in the direction of approaching the lowermost floor or the uppermost floor within the acceleration / deceleration section, the elevator control device moves between the normal position of the flyweight 17 and the trip position. The actuator device is controlled so as to displace the operation member 43 in a direction in which the rotational distance becomes smaller. In addition, the elevator control device has a large turning distance between the normal position of the flyweight 17 and the trip position when the car 4 is moved in the acceleration / deceleration section in a direction away from the lowermost floor or the uppermost floor force. The actuator device is controlled so as to displace the operation member 43 in such a direction.

Next, the operation will be described. In the elevator control device, the speed of the car 4 is constantly determined based on information from the encoder. When the car 4 is moved in the constant speed section, the operation member 43 is fixed at a predetermined position without being displaced by the actuator device. Therefore, the magnitudes of the first and second overspeeds are constant regardless of the position of the force 4.

When the car 4 is moved in the acceleration / deceleration section, the actuator device is operated by the control of the elevator control device, and the operation member 43 is displaced according to the position of the car 4. As a result, the normal position of the flyweight 17 is displaced radially outward of the governor sheave 15 as the position of the car 4 approaches the lowermost floor or the uppermost floor, and the position of the car 4 is changed to the lowermost floor or the uppermost floor. Adjustment is made so that the governor sheave 15 is displaced radially inward as the force is further away. That is, the magnitudes of the first and second overspeeds are continuously reduced as the car 4 approaches the lowermost floor or the uppermost floor, and continuously increased as the lowermost floor or the uppermost floor moves away.

[0040] During normal operation, the car 4 is moved in the hoistway 1 according to the normal speed pattern 55.

At this time, the flyweight 17 is rotated outward in the radial direction of the governor sheave 15 by the centrifugal force generated by the rotation of the governor sheave 15 according to the speed of the car 4.

[0041] When for some reason the speed of the car 4 further increases and the speed of the car 4 reaches the value of the first overspeed pattern 56, the flyweight 17 is rotated to the stop operation position, and the switch lever 22 is It is operated by the operating claw 19. As a result, the power supply to the drive device 2 is stopped by the control of the elevator control device, the brake device is operated, and the car 4 is stopped.

[0042] For example, when the main rope 3 is broken, even when the driving device 2 is stopped, the car 4 is moved without stopping, and the speed of the force 4 reaches the value of the second overspeed pattern 57. The fly weight 17 is further rotated by the centrifugal force generated by the rotation of the governor sheave 15 and reaches the trip position. As a result, the engagement claw 26 is disengaged from the trip lever 24 and rotated, and is engaged with the ratchet 25. As a result, the ratchet 25 is slightly rotated in the rotational direction of the governor sheave 15.

The rotational force of the ratchet 25 is transmitted to the arm 27 through the connection link 30, the spring shaft 29, the spring receiving member 31, and the pressing spring 32. As a result, the arm 27 is rotated, and the shoe 28 is pressed against the governor rope 11 by the pressing spring 32 after contacting the governor rope 11. Thereby, the governor rope 11 is braked.

[0044] When the movement of the governor rope 11 is stopped, the cage 4 continues to move, whereby the lever 12 is operated and the emergency stop device 7 operates.

In such an elevator speed governor 9, an adjustment lever 34 that can rotate in the circumferential direction of the speed governor sheave 15 and an operation member 43 that can be displaced in the axial direction of the sheave shaft 14 are linked to each other. 46, and the flyweight 17 is rotated by the rotation of the adjustment lever 34, so that the governor sheave 15 is rotating. However, by rotating the operation member 43 in the axial direction of the sheave shaft 14, the rotation angle of the flyweight 17 from the normal position to the trip position can be adjusted, and the first and second overspeeds can be adjusted. Size It can be easily changed according to the position of the car 4.

[0046] Thereby, in the acceleration / deceleration section provided in the vicinity of the terminal floor, the magnitudes of the first and second overspeeds can be reduced toward the terminal floor and provided between the acceleration / deceleration sections. In the constant speed zone, the magnitude of the first and second overspeeds can be made constant. Therefore, in the vicinity of the terminal floor, the first and second overspeeds can be made smaller than in the constant speed section, and the braking distance at the time of emergency stop of the force 4 can be shortened. As a result, it is possible to reduce the size of the shock absorber provided in the pit portion of the hoistway 1 and to reduce the depth dimension of the pit portion. In addition, the overhead size can be reduced to allow the car 4 to overshoot and jump. That is, the size of the hoistway 1 in the height direction can be reduced.

[0047] The interlocking mechanism 46 is provided on the outer peripheral surface of the sheave shaft 14 and the displacement body 47 integrated with the operation member 43. When the displacement body 47 is displaced with respect to the sheave shaft 14, the interlock mechanism 46 is displaced. When the displacement body 47 is displaced with respect to the sheave shaft 14, provided on the inner peripheral surface of the sheave shaft side spline portion 48 for rotating the body 47 relative to the sheave shaft 14 and the cylindrical portion 35a of the adjustment lever 34. And a lever side spline portion 49 that rotates the cylindrical portion 35a with respect to the displacement body 47 in a direction opposite to the rotation direction of the displacement body 47 by the sheave shaft side spline portion 48. A predetermined resistance force can be generated by the sheave shaft side spline portion 48 and the lever side spline portion 49 against the displacement of the displacement body 47 in the axial direction of 14, and the centrifugal force caused by the rotation of the governor sheave 15 It is possible to prevent displacement of the displacement body 47 with respect to the sheave shaft 14 due to vibration.

[0048] The displacement body 47 is spline-coupled to the sheave shaft 14 by a sheave-side spline portion 48 whose teeth are inclined with respect to the axial direction of the sheave shaft 14. Since the splined portion 49 is inclined to the cylindrical portion 35a by the lever side spline portion 49 inclined with respect to the axial direction, the displacement body 47 is displaced by the displacement of the displacement body 47 in the axial direction of the sheave shaft 14. The cylindrical portion 35a can be rotated more reliably with respect to the displacement body 47.

In the above example, the coupling of the displacement body 47 to the cylindrical portion 35a and the sheave shaft 14 is caused by the displacement of the displacement body 47 in the axial direction of the sheave shaft 14 that is a spline coupling. It is not necessary to limit to spline connection as long as 47 can be rotated. [0050] Embodiment 2.

FIG. 7 is a cross-sectional view of an essential part showing an elevator governor according to Embodiment 2 of the present invention. FIG. 8 is a main part configuration diagram showing the speed governor 9 when viewed along the radial direction of the speed governor sheave 15 in FIG. In the figure, a slide pin 61 extending in the radial direction of the governor sheave 15 is fixed to the displacement body 47 in a penetrating state. The slide pin 61 has a first projecting portion 61a that projects the inner peripheral surface force of the displacement body 47, and a second projecting portion 61b that projects the outer surface force of the displacement body 47.

[0051] On the outer peripheral surface of the sheave shaft 14, a sheave shaft side groove portion 62 into which the first projecting portion 61a is slidably inserted is provided. The sheave shaft side groove 62 is inclined with respect to the axial direction of the sheave shaft 14. The first protrusion 61a is guided along the sheave shaft side groove 62 by the displacement of the displacement body 47 in the axial direction of the sheave shaft 14. Thereby, the displacement body 47 is displaced in the axial direction of the sheave shaft 14 while being rotated with respect to the sheave shaft 14.

[0052] On the inner peripheral surface of the cylindrical portion 35a, a lever side groove portion 63 into which the second projecting portion 61b is slidably inserted is provided. The lever side groove 63 is inclined with respect to the axial direction of the sheave shaft 14 in the direction opposite to the inclination direction of the sheave shaft side groove 62. The second protrusion 61b is guided along the lever side groove 63 by the displacement of the displacement body 47 in the axial direction of the sheave shaft 14. The cylindrical portion 35a is rotated with respect to the displacement body 47 in a direction opposite to the rotation direction of the displacement body 47 by the sheave shaft side groove 62 due to the displacement of the sheave shaft 14 in the axial direction.

The inclination angle of the sheave shaft side groove 62 with respect to the axial direction of the sheave shaft 14 is different from the inclination angle of the lever side groove 63 with respect to the axial direction of the sheave shaft 14. When the displacement body 47 is displaced in the axial direction of the sheave shaft 14 relative to the sheave shaft 14, the rotation of the displacement body 47 with respect to the sheave shaft 14 and the rotation of the cylindrical portion 35a with respect to the displacement body 47 are performed simultaneously. The rotation direction of the displacement body 47 with respect to the sheave shaft 14 and the rotation direction of the cylindrical portion 35a with respect to the displacement body 47 are opposite to each other. Therefore, when the displacement body 47 is displaced in the axial direction of the sheave shaft 14, the adjustment lever 34 has a rotation angle of the displacement body 47 with respect to the sheave shaft 14 and a rotation angle of the cylindrical portion 35 a with respect to the displacement body. It is rotated with respect to the sheave axle 14 and the governor sheave 15 by the angle difference.

[0054] Note that the interlocking mechanism 64 that interlocks the operation member 43 and the adjustment lever 34 with each other includes the displacement body 4 7. It has a slide pin 61, a sheave shaft side groove 62 and a lever side groove 63. Other configurations are the same as those in the first embodiment.

In such an elevator apparatus, the sheave shaft side groove 62 that rotates the displacement body 47 with respect to the sheave shaft 14 by guiding the first projecting portion 61a that also projects the inner peripheral surface force of the displacement body 47 has the sheave shaft. A lever side groove 63 that rotates the cylindrical portion 35a with respect to the displacement body 47 by guiding the second protrusion 61b that is provided on the axle 14 and also projects the outer peripheral surface force of the displacement body 47 is an inner peripheral surface of the cylindrical portion 35a. Therefore, the structure of the interlocking mechanism 64 can be simplified, and the manufacturing cost can be reduced.

[0056] In the above example, the sheave shaft side groove portion 62 provided in the sheave shaft 14 may be a long hole. In the above example, the lever-side groove 63 is provided in the cylindrical portion 35a, but the lever-side groove 63 is a long hole.

Claims

The scope of the claims

[1] sheave axle supported rotatably on the base,

A speed governor sheave that can be rotated together with the sheave axle, wrapped around a speed governor rope that moves with the forceps,

Displaceable with respect to the governor sheave between the normal position and the trip position that is located radially outside the governor sheave with respect to the normal position. A flyweight that is displaced from the normal position to the trip position by the centrifugal force generated by the rotation of the governor sheave,

A braking mechanism that is actuated by displacement of the flyweight to the trip position and applies braking force to the governor rope;

An adjusting lever that is rotatable in a circumferential direction of the governor sheave with respect to the sheave shaft; a balance spring that biases the flyweight in a direction against the centrifugal force; the fly weight and the adjusting lever Connected body connected between,

An operation member provided on the sheave shaft and displaceable in the axial direction of the sheave shaft, and an interlocking mechanism that interlocks the operation member and the adjustment lever.

With

The adjustment lever can be rotated by the displacement of the operation member in the axial direction of the sheave shaft,

The elevator governor is characterized in that the adjustment of the distance from the normal position to the trip position is performed by rotating the adjustment lever! /.

[2] The adjustment lever includes a lever main body including a cylindrical portion through which the sheave shaft is passed, and a lever piece provided on the lever main body and connected to the coupling body.

The interlocking mechanism is provided on an annular displacement body integrated with the operation member and an outer peripheral surface of the sheave shaft, and when the displacement body is displaced with respect to the sheave shaft, the displacement body is A first guide portion that is rotated with respect to the sheave shaft, and an inner peripheral surface of the cylindrical portion, and when the displacement body is displaced with respect to the sheave shaft, the change by the first guide portion is performed. 2. The elevator speed control according to claim 1, further comprising: a second plan for rotating the cylindrical portion with respect to the displacement body in a direction opposite to a rotation direction of the position body. Machine.

[3] At least one of the first guide part and the second guide part is a spline part in which a tooth line is inclined with respect to the axial direction of the sheave shaft,

The displacement body includes at least the cylindrical portion and the sheave shaft by the spline portion.

3. The elevator governor according to claim 2, wherein the elevator governor is spline-coupled to one of the V-shifts.

[4] At least one of the first guide portion and the second guide portion is a groove portion inclined with respect to the axial direction of the sheave shaft,

The elevator governor according to claim 2, wherein the displacement body is provided with a protrusion inserted into the groove.