CN112424103B

CN112424103B - Speed limiter of elevator

Info

Publication number: CN112424103B
Application number: CN201880095739.1A
Authority: CN
Inventors: 粉川靖之
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2018-07-24
Filing date: 2018-07-24
Publication date: 2022-09-09
Anticipated expiration: 2038-07-24
Also published as: JPWO2020021629A1; CN112424103A; JP6932261B2; WO2020021629A1

Abstract

In a speed governor for an elevator, a protrusion is provided on a ratchet having a ratchet, and a hook is provided on a pawl member having an operating pawl. The releasing member applies a force to the pawl member in a direction in which the operating pawl and the hook portion are separated from the ratchet. The damper applies resistance to the pawl member when the operating pawl and the hook portion are displaced in a direction away from the ratchet. The locus of the ratchet when the ratchet rotates about the pulley shaft becomes an operation region. The operation claw is maintained in the operation region by the hooking part hooking the protrusion part.

Description

Speed limiter of elevator

Technical Field

The present invention relates to an elevator governor having a governor sheave rotated by movement of an elevating body.

Background

Conventionally, the following elevator speed governors are known: when the rotational speed of the governor sheave that rotates in accordance with the movement of the car reaches an excessive speed for emergency stop, the governor rope is gripped to stop the movement of the car. In such a conventional elevator governor, a claw provided on the governor sheave hooks the ratchet by a centrifugal force generated by rotation of the governor sheave. The governor catches the ratchet with a pawl to hold the governor rope. A spring force is applied to the pawl in a direction away from the ratchet. When the governor holds the governor rope, the pawl is disengaged from the ratchet by the spring force when the car moves upward. This can automatically release the operating state of the governor holding the governor rope (see patent document 1, for example).

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2001 and 106454

Disclosure of Invention

Problems to be solved by the invention

However, for example, when the car and the counterweight are suspended by the main ropes, if the car moving downward is brought into an emergency stop, the counterweight receives an upward inertial force. When the counterweight receives an upward inertial force, the counterweight starts to fall freely after moving upward. At this time, if the brake of the hoisting machine fails, a phenomenon occurs in which the car moves slightly upward due to free fall of the counterweight.

In the conventional elevator governor disclosed in patent document 1, when such a back vibration phenomenon occurs, the operating state of the governor holding the governor rope is erroneously released, and the car starts moving downward.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a speed governor for an elevator, which can suppress an erroneous release of an operating state in which a speed governor rope is held.

Means for solving the problems

The speed governor for an elevator of the present invention includes: a governor sheave that rotates in a 1 st direction about a sheave shaft by downward movement of the elevating body, and rotates in a 2 nd direction about the sheave shaft by upward movement of the elevating body; a ratchet having a ratchet and provided with a protrusion, the ratchet being rotatable about a rope pulley shaft independently of the governor sheave; a pawl member having an operating pawl and provided with a hook portion, the pawl member being displaced relative to the governor sheave in a direction in which the operating pawl and the hook portion approach the ratchet wheel by rotation of the governor sheave; a releasing member for applying a force to the pawl member in a direction in which the operating pawl and the hook portion are separated from the ratchet; a damper that applies resistance to the pawl member when the operating pawl and the hook portion are displaced in a direction away from the ratchet; and a braking mechanism for braking a governor rope wound around the governor sheave by an operating pawl that hooks the ratchet teeth to rotate the ratchet teeth in the 1 st direction, wherein a trajectory of the ratchet teeth when the ratchet rotates about the sheave shaft becomes an operating region, and when the operating pawl enters the operating region, the operating pawl hooks the ratchet teeth by the rotation of the governor sheave in the 1 st direction, and the operating pawl is maintained in the operating region by the rotation of the governor sheave in the 2 nd direction to hook the hooking portion to the protrusion.

Effects of the invention

According to the speed governor for an elevator of the present invention, it is possible to suppress erroneous release of the operating state of the speed governor gripping the speed governor rope.

Drawings

Fig. 1 is a side view showing an elevator according to embodiment 1 of the present invention.

Fig. 2 is a front view showing the governor of fig. 1.

Fig. 3 is a front view showing a part of the structure of the governor of fig. 2.

Fig. 4 is an enlarged front view showing a state in which the operating pawl of fig. 3 is hooked on the ratchet.

Fig. 5 is an enlarged front view showing a state in which the reverse pawl of fig. 4 is hooked on the reverse tooth.

Fig. 6 is an enlarged front view showing a state in which the reverse pawl of fig. 4 is offset radially outward from the reverse tooth.

Fig. 7 is an enlarged front view showing a ratchet and a pawl member of an elevator governor in embodiment 2 of the present invention.

Fig. 8 is a top view showing the ratchet and pawl component of fig. 7.

Fig. 9 is a side view showing the ratchet and pawl member of fig. 7.

Detailed Description

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

Embodiment 1.

Fig. 1 is a side view showing an elevator according to embodiment 1 of the present invention. In the figure, a car 2 and a counterweight 3 are provided in a hoistway 1. The car 2 and the counterweight 3 are vertically movable bodies in the hoistway 1. A hoisting machine 4 as a driving device is provided in an upper portion in the hoistway 1, and the hoisting machine 4 generates a driving force for moving the car 2 and the counterweight 3 in the vertical direction.

A plurality of main ropes 5 as a suspension body suspending the car 2 and the counterweight 3 are wound around a drive sheave of the hoisting machine 4. As the suspension body, a belt may be used instead of a rope.

The car 2 and the counterweight 3 are moved in the vertical direction in the hoistway 1 by rotation of the drive sheave of the hoisting machine 4. The moving direction of the car 2 and the moving direction of the counterweight 3 are opposite to each other. That is, when the car 2 moves upward, the counterweight 3 moves downward, and when the car 2 moves downward, the counterweight 3 moves upward. When the car 2 and the counterweight 3 move in the hoistway 1, the car 2 is guided by the car guide rails 6, and the counterweight 3 is guided by the counterweight guide rails, not shown.

An emergency stop device 7 is provided at a lower portion of the car 2. The emergency stop device 7 is provided with an operation arm 8. The emergency stop device 7 grips the car guide rail 6 by operation of the operation arm 8. Downward movement of the car 2 is prevented by gripping of the car guide rail 6 by the safety device 7.

A speed limiter 9 is provided in an upper portion in the hoistway 1. In this example, the speed limiter 9 is supported by a speed limiter table 12 fixed to an upper portion of the car guide rail 6. A tension pulley 10 is provided at a lower portion in the hoistway 1. A governor rope 11 is wound around the governor 9 and the tension pulley 10. Both ends of the governor rope 11 are connected to the operating arm 8. Thereby, the governor rope 11 is looped between the governor 9 and the tension sheave 10. The governor rope 11 moves along with the movement of the car 2.

The governor 9 can grip the governor rope 11. When the speed governor 9 grips the governor rope 11 when the car 2 moves downward, the operating arm 8 is operated by the governor rope 11.

Fig. 2 is a front view showing governor 9 of fig. 1. Fig. 3 is a front view showing a part of the structure of governor 9 in fig. 2. A support member 21 is fixed to the upper surface of the governor base 12. A sheave shaft 22 is horizontally fixed to the support member 21. A speed limiter sheave 23 is rotatably provided on the sheave shaft 22. The governor rope 11 is wound around the governor sheave 23. The governor sheave 23 rotates about the sheave shaft 22 in accordance with the movement of the car 2 and the governor rope 11. That is, the governor sheave 23 rotates in the 1 st direction a, which is the counterclockwise direction in fig. 2, by the downward movement of the car 2. The governor sheave 23 is rotated in the 2 nd direction B, which is the clockwise direction in fig. 2, by the upward movement of the car 2. The rotation speed of the governor sheave 23 is a speed corresponding to the moving speed of the car 2.

The governor sheave 23 is provided with a pair of support shafts 26. Each support shaft 26 is disposed parallel to the sheave shaft 22. The flyweights 25 are rotatably attached to the support shafts 26, respectively. That is, the governor sheave 23 is provided with a pair of flyweights 25 that are individually rotatable about a pair of support shafts 26.

Each flyweight 25 rotates about the support shaft 26 in accordance with a centrifugal force generated by the rotation of the governor sheave 23. That is, each flyweight 25 is displaced relative to the governor sheave 23 in accordance with the rotational speed of the governor sheave 23.

The two flyweights 25 are coupled to each other by a link 27. Further, a balance spring 28 as an elastic body that resists a centrifugal force is provided between the one flyweight 25 and the governor sheave 23. When the rotation speed of the governor sheave 23 increases, the flyweights 25 are displaced relative to the governor sheave 23 against the elastic restoring force of the balance spring 28.

An operation piece 29 is fixed to one flyweight 25. The operation piece 29 protrudes radially outward from the one flyweight 25. One flyweight 25 is displaced relative to the governor sheave 23 against the elastic restoring force of the balance spring 28, and the operating piece 29 moves in a direction away from the sheave shaft 22.

A switch 30 including an operating lever is attached to the support member 21. The switch 30 outputs a stop signal to a control device, not shown, by operating the operation lever. The control device stops the power supply to the hoisting machine 4 by receiving the stop signal from the switch 30, and operates the brake of the hoisting machine 4, not shown.

The tip end of the operating lever of the switch 30 is disposed on the track of the operating piece 29 when the speed of the car 2 becomes a set excessive speed higher than the normal speed. Therefore, when the speed of the car 2 becomes a set excessive speed, the operating lever of the switch 30 is operated by the operating piece 29.

A claw member 31 is provided on one support shaft 26. The claw member 31 is rotatable about the support shaft 26 independently of the flyweight 25. Thereby, the pawl member 31 is provided to the governor sheave 23 via the support shaft 26 so as to be displaceable. As shown in fig. 3, the claw member 31 includes a claw member body portion 311 provided on the support shaft 26 and an operating claw 312 provided on the claw member body portion 311.

The operating pawl 312 protrudes from the pawl member body 311 in the 1 st direction a toward the sheave shaft 22. The operating pawl 312 is provided with a reverse pawl 313 serving as a hook portion. The reverse pawl 313 protrudes from the operating pawl 312 in the 2 nd direction B.

A ratchet 24 is rotatably provided on the sheave shaft 22. The ratchet 24 is disposed radially inward of the pawl member 31. Further, the ratchet 24 is rotatable about the sheave shaft 22 independently of the governor sheave 23. The ratchet 24 includes a disc-shaped ratchet main body portion 241 provided on the sheave shaft 22, and a plurality of ratchet teeth 242 provided on an outer peripheral portion of the ratchet main body portion 241.

The plurality of ratchet teeth 242 are arranged at equal intervals in the circumferential direction of the ratchet 24. Further, each ratchet tooth 242 protrudes from the outer peripheral portion of the ratchet main body portion 241 in the 2 nd direction B in a direction away from the sheave shaft 22. Each ratchet tooth 242 is provided with a reverse tooth 243 as a projection. The reverse teeth 243 protrude from each ratchet tooth 242 in the 1 st direction a. Thus, in the ratchet wheel 24, the reverse teeth 243 are located between the respective tooth tops of the two ratchet teeth 242 adjacent to each other.

As shown in fig. 2, a torsion spring 32 as an elastic body is provided between the governor sheave 23 and the pawl member 31. One end of the torsion spring 32 is connected to the governor sheave 23. The other end of the torsion spring 32 is connected to the claw member 31. The torsion spring 32 is a releasing member that applies a force to the pawl member 31 in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24. In this example, the torsion spring 32 generates an elastic restoring force that rotates the pawl member 31 in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24.

A stopper pin 33 to which a part of the claw member 31 is hooked is provided to one of the flyweights 25. Displacement of the claw member 31 by the elastic restoring force of the torsion spring 32 is prevented by a part of the claw member 31 hooking the stopper pin 33.

In a state where a part of the claw member 31 is hooked on the stopper pin 33, the claw member 31 is displaced relative to the governor sheave 23 integrally with the one flyweight 25.

The pawl member 31 is displaced in a direction in which the operating pawl 312 and the counter pawl 313 approach the ratchet 24 by displacement of the flyweight 25 in a direction opposite to the elastic restoring force of the balance spring 28. Therefore, the claw member 31 receives a centrifugal force caused by the rotation of the governor sheave 23 via the flyweight 25, and is displaced in a direction in which the operating claw 312 and the counter claw 313 approach the ratchet 24 against the elastic restoring force of the balance spring 28.

Further, the pawl member 31 is displaced in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24 by the displacement of the flyweight 25 in the same direction as the elastic restoring force of the balance spring 28. That is, the pawl member 31 receives the elastic restoring force of the balance spring 28 via the flyweight 25, and is displaced in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24.

A damper 34 that applies a resistance force to the pawl member 31 when the pawl member 31 is displaced relative to the governor sheave 23 is provided on the support shaft 26 on which the pawl member 31 is provided. The damper 34 applies resistance to the pawl member 31 when rotating about the support shaft 26. That is, the damper 34 generates a resistance force against the rotational force of the claw member 31. In this example, the damper 34 applies resistance to the pawl member 31 regardless of which direction the pawl member 31 is displaced in the direction in which the operating pawl 312 and the reversing pawl 313 approach the ratchet 24 or the direction in which the operating pawl 312 and the reversing pawl 313 separate from the ratchet 24.

When the pawl member 31 is displaced in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24, the magnitude of the resistance applied to the pawl member 31 by the damper 34 is larger than when the pawl member 31 is displaced in a direction in which the operating pawl 312 and the reverse pawl 313 move toward the ratchet 24. In this example, an oil type rotary damper that applies resistance to the claw member 31 by the resistance of oil is used as the damper 34.

When the rotation speed of the governor sheave 23 increases, the centrifugal force applied to the flyweight 25 increases. Thereby, the pawl member 31 is displaced relative to the governor sheave 23 in a direction in which the operating pawl 312 and the counter pawl 313 approach the ratchet 24. When the speed of the car 2 becomes an excessive speed of emergency stop higher than a set excessive speed when the car 2 moves downward, the operating pawl 312 hooks any one of the plurality of ratchet teeth 242, and the ratchet 24 rotates in the 1 st direction a together with the governor sheave 23.

The support member 21 is provided with a brake mechanism 35 that brakes the governor rope 11. The brake mechanism 35 includes an interlocking mechanism portion 351 interlocked with the rotation of the ratchet 24, and a brake shoe 352 provided to the interlocking mechanism portion 351.

The brake shoe 352 is disposed radially outward of the governor sheave 23. The brake shoe 352 faces the outer peripheral portion of the governor sheave 23 via the governor rope 11.

The interlocking mechanism 351 is connected to the ratchet 24 and the support member 21. Further, the ratchet 24 rotates in the 1 st direction a, and the interlocking mechanism 351 presses the brake shoe 352 against the outer peripheral portion of the governor sheave 23 via the governor rope 11. That is, the interlocking mechanism 351 is rotated in the 1 st direction a by the ratchet 24, and grips the governor rope 11 between the governor sheave 23 and the brake shoe 352. The speed governor rope 11 is held between the speed governor sheave 23 and the brake shoe 352 and is braked.

Fig. 4 is an enlarged front view showing a state in which the operating pawl 312 of fig. 3 is hooked on the ratchet 242. The locus of the ratchet teeth 242 when the ratchet 24 rotates about the pulley shaft 22 becomes an annular operation region S1 centered about the pulley shaft 22. The operation region S1 is a region between the locus of the tooth tips of the ratchet teeth 242 and the locus of the tooth roots of the ratchet teeth 242.

Each reverse tooth 243 is disposed corresponding to the circumferential position of each ratchet tooth 242. Thereby, the tooth tips of the ratchet teeth 242 and the tooth tips of the reverse teeth 243 are alternately arranged in the circumferential direction of the ratchet 24. Further, each reverse tooth 243 is located within the action region S1.

When the operating claw 312 is located at a position radially outward of the operating region S1, the operating claw 312 does not hook the ratchet 24 even if the governor sheave 23 rotates. Therefore, when the operating pawl 312 is located at a position deviated from the operating region S1, the ratchet wheel 24 does not rotate even if the governor sheave 23 rotates.

When the operating pawl 312 enters the operating region S1, the governor sheave 23 rotates in the 1 st direction a, and the operating pawl 312 hooks the ratchet tooth 242. In a state where the operating pawl 312 is hooked on the ratchet teeth 242, the operating pawl 312 reaches the root of the ratchet teeth 242. Further, in a state where the operating pawl 312 is hooked on the ratchet tooth 242, the tip end portion of the reverse pawl 313 is located radially inward of the sheave shaft 22 from the tip of the reverse tooth 243.

While the tip end of the counter claw 313 is maintained at a position radially inward of the tooth tip position of the counter tooth 243, the speed governor sheave 23 rotates in the 2 nd direction B, and the counter claw 313 hooks the counter tooth 243. The position of the reverse pawl 313 when the reverse pawl 313 hooks the reverse tooth 243 is radially outward of the position of the reverse pawl 313 when the operating pawl 312 hooks the ratchet 242.

When the governor sheave 23 is rotated in the 2 nd direction B from the state where the operating pawl 312 is hooked on the ratchet teeth 242, the operating pawl 312 is disengaged from the ratchet teeth 242. The operating pawl 312 disengaged from the ratchet teeth 242 is displaced outward in the radial direction away from the ratchet 24 by the elastic restoring force of the torsion spring 32 while being subjected to the resistance of the damper 34.

After the operating pawl 312 is disengaged from the ratchet teeth 242, the time until the tip end of the reverse pawl 313 is shifted radially outward from the position of the tip of the reverse tooth 243 is adjusted to the 2 nd direction set time by adjusting the resistance of the damper 34. Therefore, when the operating pawl 312 is disengaged from the ratchet teeth 242, the reverse pawl 313 hooks the reverse tooth 243 by the reverse pawl 313 reaching the circumferential position of the reverse tooth 243 within the 2 nd-direction set time.

On the other hand, after the operating pawl 312 is disengaged from the ratchet teeth 242, the reverse pawl 313 is displaced radially outward from the reverse teeth 243 when the 2 nd direction setting time has elapsed while maintaining the state in which the reverse pawl 313 is disengaged from the reverse teeth 243 and the state in which the operating pawl 312 is disengaged from the ratchet teeth 242. Thereby, the operating pawl 312 is displaced radially outward from the operating region S1.

Fig. 5 is an enlarged front view showing a state in which the reverse pawl 313 of fig. 4 is hooked on the reverse tooth 243. In a state where the reverse pawl 313 hooks the reverse tooth 243, the reverse pawl 313 meshes with the reverse tooth 243 not only in the circumferential direction of the ratchet wheel 24 but also in the radial direction of the ratchet wheel 24. This prevents the pawl member 31 from being displaced in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24. Therefore, the operating pawl 312 is maintained in the operating region S1 by the reverse pawl 313 hooking the reverse tooth 243.

When the speed governor sheave 23 rotates in the 1 st direction a from the state where the reverse pawl 313 catches the reverse tooth 243, the reverse pawl 313 disengages from the reverse tooth 243. After the reverse pawl 313 is disengaged from the reverse tooth 243, the time until the tip end portion of the operating pawl 312 deviates from the operating region S1 is adjusted to the 1 st direction setting time by adjusting the resistance of the damper 34. When the reverse pawl 313 is disengaged from the reverse teeth 243, the operating pawl 312 hooks the ratchet teeth 242 by the operating pawl 312 reaching the circumferential position of the ratchet teeth 242 within the 1 st direction setting time.

The magnitude of the resistance force applied to the pawl member 31 by the damper 34 is adjusted in accordance with the speeds of the operating pawl 312 and the counter pawl 313 when displaced in the direction away from the ratchet 24 and the rotational speed of the governor sheave 23 assumed in the ringing phenomenon.

That is, the magnitude of the resistance force applied to the claw member 31 by the damper 34 is adjusted to: when the speed governor sheave 23 rotates in the 2 nd direction B due to the ringing phenomenon, the time until the reversing pawls 313 reach the circumferential positions of the reversing teeth 243 is within the 2 nd direction setting time. Further, the magnitude of the resistance force applied to the claw member 31 by the damper 34 is adjusted to: when the governor sheave 23 rotates in the 1 st direction a due to the ringing phenomenon, the time until the operating pawl 312 reaches the circumferential position of the ratchet teeth 242 falls within the 1 st direction set time.

The governor 9 includes a support member 21, a sheave shaft 22, a governor sheave 23, a ratchet 24, a flyweight 25, a link 27, a balance spring 28, a switch 30, a pawl member 31, a torsion spring 32, a damper 34, and a brake mechanism 35.

Next, the operation will be described. When the car 2 moves downward, the governor sheave 23 rotates in the 1 st direction a, i.e., counterclockwise in fig. 2, about the sheave shaft 22 in accordance with the movement of the car 2. Thereby, each flyweight 25 receives a centrifugal force corresponding to the rotation speed of the governor sheave 23.

When the centrifugal force applied to each flyweight 25 increases as the moving speed of the car 2 increases, each flyweight 25 rotates about the support shaft 26 against the elastic restoring force of each of the balance spring 28 and the torsion spring 32. As a result, the operating piece 29 is gradually displaced outward in the radial direction of the governor sheave 23, and the radius of the orbit of the operating piece 29 gradually increases. At this time, the operating pawl 312 and the reverse pawl 313 are displaced in a direction approaching the ratchet 24.

Thereafter, when the rotational speed of the governor sheave 23 reaches a set excessive speed due to some abnormality, the radius of the rotational orbit of the operating piece 29 reaches the radius of the operating lever passing through the switch 30. Thereby, the operation lever of the switch 30 is operated by the operation piece 29. When the operating lever of the switch 30 is operated by the operating piece 29, the power supply to the hoisting machine 4 is stopped, and the brake of the hoisting machine 4 is operated.

When the car 2 continues to move downward after the supply of power to the hoisting machine 4 is stopped, the speed of the car 2 continues to increase. In this case, when the speed of the car 2 reaches the emergency stop excessive speed higher than the set excessive speed, the operating claw 312 enters the operating region S1. At this time, since the governor sheave 23 rotates in the 1 st direction a, the operating pawl 312 hooks the ratchet tooth 242 as shown in fig. 4.

When the operating pawl 312 hooks the ratchet tooth 242, the ratchet 24 rotates in the 1 st direction a together with the governor sheave 23. When the ratchet 24 rotates in the 1 st direction a, the brake mechanism 35 operates, and the governor rope 11 is gripped between the governor sheave 23 and the brake shoe 352. Thereby, the governor rope 11 is braked, and the movement of the governor rope 11 is stopped. At this time, the operating pawl 312 remains hooked to the ratchet 242. On the other hand, each flyweight 25 is returned to the original position by the elastic restoring force of the balance spring 28.

When the movement of the governor rope 11 is stopped, the operating arm 8 is operated, and the emergency stop device 7 is operated. This causes the downward movement of the car 2 to stop urgently.

When the downward movement of the car 2 is stopped suddenly, the counterweight 3 receives an upward inertial force. Thereby, the counterweight 3 moves upward. After that, the counterweight 3 starts to fall freely. At this time, if the operation of the brake of the hoisting machine 4 is incomplete due to a failure of the brake of the hoisting machine 4 or the like, a phenomenon of a return vibration occurs in which the car 2 moves slightly upward due to free fall of the counterweight 3.

When the ringing phenomenon occurs, the governor sheave 23 rotates in the 2 nd direction B. Thereby, the operation pawl 312 is disengaged from the ratchet teeth 242.

When the operating pawl 312 is disengaged from the ratchet teeth 242, the pawl member 31 is displaced in a direction in which the operating pawl 312 and the reverse pawl 313 are separated from the ratchet 24 by the elastic restoring force of the torsion spring 32. At this time, the pawl member 31 is displaced relative to the governor sheave 23 while receiving the resistance of the damper 34. This suppresses the speed of displacement of the pawl member 31 in the direction in which the operating pawl 312 and the reverse pawl 313 leave the ratchet 24.

On the other hand, when the ringing phenomenon occurs, the governor sheave 23 rotates in the 2 nd direction B, so that the operating pawl 312 is disengaged from the ratchet teeth 242, and the reverse pawl 313 moves toward the reverse tooth 243. At this time, since the displacement speed of the pawl member 31 with respect to the governor sheave 23 is suppressed by the resistance of the damper 34, the tip end portion of the reverse pawl 313 is maintained at a position radially inward of the tooth tip of the reverse tooth 243, and the reverse pawl 313 reaches the circumferential position of the reverse tooth 243. Thereby, the reverse pawl 313 hooks the reverse tooth 243. As a result, the state in which the operating pawl 312 and the reverse pawl 313 enter the operating region S1 is maintained.

After the reversing claw 313 hooks the reversing tooth 243, when the rotation direction of the governor sheave 23 is changed from the 2 nd direction B to the 1 st direction a by the weight of the car 2, the reversing claw 313 is disengaged from the reversing tooth 243. Thereafter, the governor sheave 23 is rotated in the 1 st direction a, so that the pawl member 31 moves toward the ratchet teeth 242, and the operating pawl 312 is again hooked on the ratchet teeth 242 in the operating region S1. At this time, the displacement speed of the pawl member 31 relative to the governor sheave 23 is also suppressed by the resistance of the damper 34. This prevents the operating state of the governor 9 gripping the governor rope 11 from being released.

Next, an operation when the operating state of the governor 9 holding the governor rope 11 is released will be described. Fig. 6 is an enlarged front view showing a state in which the reverse pawl 313 is shifted radially outward from the reverse tooth 243 in fig. 4. When the operating state of the governor 9 is released, the car 2 is moved upward at a speed lower than the speed at which the car 2 is supposed to move upward in the return vibration phenomenon.

When the car 2 moves upward, the governor sheave 23 rotates in the 2 nd direction B. Thereby, the operation pawl 312 is disengaged from the ratchet teeth 242.

When the operating pawl 312 is disengaged from the ratchet teeth 242, the operating pawl 312 and the reverse pawl 313 move toward the reverse teeth 243 and are displaced in a direction away from the ratchet 24 by the elastic restoring force of the torsion spring 32 while receiving the resistance force of the damper 34. At this time, since the speed of rotation of the governor sheave 23 in the 2 nd direction B is lower than that in the chattering phenomenon, the reversing pawls 313 are displaced radially outward relative to the reversing teeth 243 before the reversing pawls 313 reach circumferential positions of the reversing teeth 243. At this time, the rotation of the governor sheave 23 may be stopped until the reversing pawl 313 is displaced radially outward from the reversing teeth 243.

Thereby, the reverse pawl 313 is prevented from hooking the reverse tooth 243, and the operating pawl 312 and the reverse pawl 313 deviate from the operating region S1. As a result, the pawl member 31 is disengaged from the ratchet 24, and the operating state of the governor 9 is released.

In the governor 9, the reverse teeth 243 are provided on the ratchet 24, and the reverse pawl 313 is provided on the pawl member 31. Further, the damper 34 applies a resistance force to the pawl member 31 when the operating pawl 312 and the reverse pawl 313 are displaced in a direction away from the ratchet 24. Therefore, even if the operating pawl 312 is disengaged from the ratchet teeth 242, the speed of the pawl member 31 that displaces the operating pawl 312 and the reverse pawl 313 in the direction away from the ratchet 24 can be suppressed. Thus, even when the ringing phenomenon occurs, the reverse pawl 313 can be hooked on the reverse tooth 243 before the operating pawl 312 deviates from the operating region S1. Therefore, even when the ringing phenomenon occurs, the state in which the operating pawl 312 enters the operating region S1 can be maintained, and the operating state of the governor 9 holding the governor rope 11 can be suppressed from being erroneously released.

Further, by maintaining the state in which the operating pawl 312 is disengaged from the ratchet teeth 242 and the state in which the reverse pawl 313 is disengaged from the reverse tooth 243, the reverse pawl 313 can be displaced radially outward from the reverse tooth 243 by the elastic restoring force of the torsion spring 32. This allows operating pawl 312 to be disengaged from operating region S1, and the operating state of governor 9 can be easily released.

Further, the reverse teeth 243 provided as the projections to the ratchet 24 are located in the operation region S1. Therefore, the reverse teeth 243 can be arranged within the rotation range of the ratchet wheel 24. This prevents the governor 9 from becoming larger due to the addition of the reverse teeth 243 to the ratchet 24.

Further, the damper 34 is a rotary damper that generates a resistance force against the rotational force of the claw member 31. Therefore, the damper 34 can be provided on the support shaft 26 on which the claw member 31 is rotatably provided. This can reduce the installation space of damper 34, and prevent governor 9 from becoming larger.

Further, when the pawl member 31 is displaced in a direction in which the operating pawl 312 and the reversing pawl 313 move away from the ratchet 24, the magnitude of the resistance force applied to the pawl member 31 by the damper 34 is larger than when the pawl member 31 is displaced in a direction in which the operating pawl 312 and the reversing pawl 313 move toward the ratchet 24. Therefore, the pawl member 31 can be easily displaced in the direction in which the operating pawl 312 approaches the ratchet 24. Thus, when the rotational speed of the governor sheave 23 reaches an excessive speed for emergency stop, the operating pawl 312 can be easily hooked on the ratchet teeth 242. Further, when the operating pawl 312 is disengaged from the ratchet teeth 242, the pawl member 31 can be made difficult to displace in a direction in which the reverse pawl 313 separates from the ratchet 24. This makes it possible to facilitate the reverse pawl 313 to catch the reverse tooth 243 when the ringing phenomenon occurs.

In the above example, the magnitude of the resistance of the damper 34 is larger when the operating pawl 312 and the reversing pawl 313 move away from the ratchet 24 than when the operating pawl 312 and the reversing pawl 313 move closer to the ratchet 24. However, the resistance force applied to the pawl member 31 by the damper 34 may be the same when the operating pawl 312 and the reverse pawl 313 approach the ratchet 24 and when the operating pawl 312 and the reverse pawl 313 leave the ratchet 24. Further, the resistance of the damper 34 applied to the pawl member 31 when the operating pawl 312 and the reverse pawl 313 approach the ratchet 24 can be eliminated.

Embodiment 2.

Fig. 7 is an enlarged front view showing a ratchet and a pawl member of an elevator governor according to embodiment 2 of the present invention. Further, fig. 8 is a plan view showing the ratchet and pawl member of fig. 7. Also, fig. 9 is a side view showing the ratchet and pawl member of fig. 7. In the present embodiment, the plurality of pins 41 are fixed to the ratchet 24 as protrusions, and the arm 42 is fixed to the pawl member 31 as a hook.

The plurality of pins 41 are arranged at equal intervals in the circumferential direction of the ratchet 24 corresponding to the circumferential positions of the plurality of ratchet teeth 242. Each pin 41 projects from a side surface of the ratchet wheel 24 in a direction intersecting a plane perpendicular to the axis of the sheave shaft 22. In this example, a plurality of pins 41 arranged parallel to the axis of the sheave shaft 22 protrude from the ratchet 24. Further, the respective pins 41 project in the same direction from the side surface of the ratchet 24. Each pin 41 is disposed on the inner peripheral edge of the operation region S1.

The arm 42 is fixed to the side of the claw member 31. Further, the arm 42 is an L-shaped member that protrudes from a side surface of the pawl member 31 and is bent toward the ratchet 24. The front end of the arm 42 is located radially inward of the sheave shaft 22 than the front end of the operating pawl 312.

When the governor sheave 23 is rotated in the 2 nd direction B in a state where the tip end of the retaining arm 42 is located radially inward of the position of the pin 41, the arm 42 hooks the pin 41. The position of the arm 42 when the arm 42 hooks the pin 41 is located radially outward of the position of the arm 42 when the operating pawl 312 hooks the ratchet 242.

After the operating pawl 312 is disengaged from the ratchet 242, the time until the distal end portion of the arm 42 is displaced radially outward from the position of the pin 41 is adjusted to the 2 nd direction setting time by adjusting the resistance of the damper 34. Therefore, when the operating pawl 312 is disengaged from the ratchet 242, the arm 42 hooks the pin 41 by the arm 42 reaching the circumferential position of the pin 41 within the 2 nd direction setting time.

On the other hand, after the operating pawl 312 is disengaged from the ratchet teeth 242, the arm 42 is displaced radially outward from the pin 41 when the 2 nd direction setting time has elapsed while maintaining the state in which the arm 42 is disengaged from the pin 41 and the state in which the operating pawl 312 is disengaged from the ratchet teeth 242. Thereby, the operation claws 312 are displaced outward in the radial direction from the operation region S1.

In a state where the arm 42 is hooked on the pin 41, the arm 42 is engaged with the pin 41 not only in the circumferential direction of the ratchet 24 but also in the radial direction of the ratchet 24. This prevents the pawl member 31 from being displaced in a direction in which the operating pawl 312 and the arm 42 are separated from the ratchet 24. The operating pawl 312 is maintained in the operating region S1 by the arm 42 hooking the pin 41.

When the governor sheave 23 is rotated in the 1 st direction a from a state where the arm 42 hooks the pin 41, the arm 42 is disengaged from the pin 41. After the arm 42 is disengaged from the pin 41, the time until the distal end portion of the operating pawl 312 deviates from the operating region S1 is adjusted to the 1 st direction setting time by adjusting the resistance of the damper 34. When the arm 42 is disengaged from the pin 41, the operating pawl 312 hooks the ratchet teeth 242 by the operating pawl 312 reaching the circumferential position of the ratchet teeth 242 within the 1 st direction setting time.

When the operating state of the speed governor 9 is released, the rotation speed of the speed governor sheave 23 is adjusted to maintain the state in which the operating pawl 312 is disengaged from the ratchet teeth 242 and the state in which the arm 42 is disengaged from the pin 41. This prevents the arm 42 from hooking the pin 41, and the operating pawl 312 from deviating from the operating region S1. Other structures and operations are the same as those of embodiment 1.

In the speed governor 9, a pin 41 arranged parallel to the axis of the sheave shaft 22 protrudes from the ratchet 24. Therefore, the position of the pin 41 can be freely set without being limited to the operation region S1.

In the above example, the pin 41 arranged parallel to the axis of the sheave shaft 22 protrudes from the ratchet 24. However, the pin 41 inclined with respect to a plane perpendicular to the axis of the sheave shaft 22 may be projected from the ratchet 24.

In the above example, the magnitude of the resistance of the damper 34 is larger when the operating pawl 312 and the arm 42 are away from the ratchet 24 than when the operating pawl 312 and the arm 42 are close to the ratchet 24. However, the resistance force applied to the pawl member 31 by the damper 34 may be the same when the operating pawl 312 and the arm 42 approach the ratchet 24 and when the operating pawl 312 and the arm 42 move away from the ratchet 24. Further, the resistance of the damper 34 applied to the pawl member 31 when the operating pawl 312 and the arm 42 approach the ratchet 24 can be eliminated.

In each of the above embodiments, the damper 34 is an oil type rotary damper. However, a friction type rotary damper may be used as the damper 34, for example. Further, an oil type damper or a friction type damper including a piston and a cylinder may also be used as the damper 34.

Further, in each of the above embodiments, the torsion spring 32 is used as the releasing member. However, an elastic body such as a coil spring or a plate spring may be used as the release member.

In each of the above embodiments, the claw member 31 is a member different from the one flyweight 25. However, the claw member 31 may be formed integrally with one flyweight 25. In this case, the torsion spring 32 may be absent. In this case, the balance spring 28 is used as a releasing member for applying a force to the pawl member 31 in a direction in which the operating pawl 312 and the reverse pawl 313 move away from the ratchet 24.

In each of the above embodiments, the speed governor 9 operates the safety device 7 provided in the car 2. However, an emergency stop device may be provided in the counterweight 3, and the governor 9 may operate the emergency stop device provided in the counterweight 3. In this case, the counterweight 3 moves downward, whereby the governor sheave 23 rotates in the 1 st direction a, and the counterweight 3 moves upward, whereby the governor sheave 23 rotates in the 2 nd direction B.

In each of the above embodiments, the speed limiter 9 is provided in the hoistway 1 of a machine-roomless elevator in which no machine room is provided. However, the speed governor 9 may be applied to an elevator in which a machine room is provided in an upper part of a hoistway. In this case, the governor 9 is provided in the machine room of the elevator.

Description of the reference symbols

2: a car (lifting body); 3: a counterweight (lifting body); 11: a governor rope; 22: a rope pulley shaft; 23: a governor sheave; 24: a ratchet wheel; 26: a support shaft; 28: a balance spring (release member); 31: a claw member; 32: a torsion spring (release member); 34: a damper; 35: a brake mechanism; 41: a pin (protrusion); 42: an arm (hook portion); 242: a ratchet; 243: reverse teeth (protrusions); 312: an actuating pawl; 313: a reversing pawl (hook).

Claims

1. A speed governor of an elevator, comprising:

a governor sheave that rotates in a 1 st direction about a sheave shaft by downward movement of a lifting body and rotates in a 2 nd direction about the sheave shaft by upward movement of the lifting body;

a ratchet wheel having a ratchet and provided with a projection, the ratchet wheel being rotatable about the rope pulley shaft independently of the governor sheave;

a pawl member that has an operation pawl and is provided with a hook, and that is displaced relative to the speed governor sheave in a direction in which the operation pawl and the hook approach the ratchet by rotation of the speed governor sheave;

a releasing member that applies a force to the pawl member in a direction in which the operating pawl and the hook portion move away from the ratchet;

a damper that applies resistance to the pawl member when the operating pawl and the hook portion are displaced in a direction away from the ratchet; and

a braking mechanism that brakes a governor rope wound around the governor sheave by the operating pawl hooking the ratchet teeth to rotate the ratchet wheel in the 1 st direction,

the track of the ratchet becomes an operation region when the ratchet rotates around the pulley shaft,

when the operating pawl enters the operating area, the operating pawl is hooked to the ratchet by the rotation of the governor sheave in the 1 st direction,

when the governor sheave is rotated in the 2 nd direction, the speed of displacement of the pawl member relative to the governor sheave is suppressed by the resistance force applied by the damper, and the hook portion is hooked on the projection, so that the operating pawl is maintained in the operating region.

2. The speed governor of an elevator of claim 1,

the protrusion is located within the action region.

3. The speed governor of an elevator of claim 1,

the protrusion protrudes from the ratchet wheel in a direction intersecting a plane perpendicular to the axis of the sheave shaft.

4. The speed governor of an elevator of claim 1,

the pawl member is formed so as to be rotatable about a support shaft provided on the governor sheave,

the damper is a rotary damper that generates a resistance force opposite to a rotational force of the claw member.

5. The speed governor of an elevator according to claim 2,

6. The speed governor of an elevator of claim 3,

7. The speed governor of an elevator according to any of claims 1 to 6,

when the pawl member is displaced in a direction in which the operating pawl and the hook portion move away from the ratchet, a magnitude of a resistance force applied to the pawl member by the damper is larger than that when the pawl member is displaced in a direction in which the operating pawl and the hook portion move toward the ratchet.