KR100816172B1 - Elevator apparatus - Google Patents

Abstract

A governor sheave which is rotatable integrally with the sheave shaft is supported by the pedestal. The governor sheave is provided with a fly weight which is displaced from the passage position to the travel position by centrifugal force due to the rotation of the governor sheave. The sheave shaft is provided with an adjustment lever that can rotate in the circumferential direction of the governor sheave. A connecting body having a balanced spring for pressing the fly weight in a direction against the centrifugal force is connected between the fly weight and the adjustment lever. The sheave shaft is provided with an operation member which can be displaced in the axial direction of the sheave shaft. The adjustment lever is rotatable by the displacement of the operation member in the axial direction of the sheave shaft. Therefore, adjustment of the distance with respect to the travel position of a normal position is performed by rotation of an adjustment lever.

Description

Elevator device {ELEVATOR APPARATUS}

The present invention relates to a governor of an elevator having a governor sheave rotated with movement of a car.

In a conventional elevator governor, the flyweight provided in the governor sheave may be rotated by the centrifugal force by the rotation of the governor sheave in order to detect that the speed of the car has reached a predetermined overspeed. An emergency stop device for preventing the car from falling is mounted on the car. The governor rope is wound around the governor sheave connected to the emergency stop device. Thus, the governor sheave is rotated at a speed corresponding to the speed of the car.

In this conventional elevator governor, when the rotation speed of the governor sheave becomes the first overspeed, the car stop switch is activated by the rotation of the fly weight. By the operation of the car stop switch, the power supply of the drive device of the elevator is cut off, and the car is stopped by the brake device of the drive device. When the rotational speed of the governor sheave reaches the second overspeed, the fly weight is further rotated, and the braking mechanism for braking the governor rope is operated. By the operation of the braking mechanism, the governor rope is braked, and the emergency stop device is operated by braking the governor rope (see Patent Document 1).

Patent Document 1: Japanese Patent Application Laid-Open No. 2001-106454

However, in such a conventional elevator governor, the setting of the first and second overspeeds cannot be adjusted during operation of the elevator. Therefore, the overspeed set in the governor becomes constant regardless of the position of the car. As a result, the governor cannot normally be operated until the speed of the car becomes extremely high even when the car is moving in the upper and lower portions of the hoistway where the speed of the car becomes low. Therefore, it is impossible to reduce the size of the shock absorber for cushioning the impact on the car and to reduce the depth dimension of the pit portion of the hoistway provided with the shock absorber. Moreover, the overhead dimension for allowing the car to pass or jump also becomes large, and the overhead dimension cannot be reduced.

This invention is made | formed in order to solve the above subjects, and an object of this invention is to obtain the speed governor of an elevator which can easily adjust the set overspeed for making emergency stop of a car.

The governor of the elevator according to the present invention is provided on a governor sheave, a governor sheave which is rotatable integrally with the sheave shaft, and is provided with a sheave shaft supported by a rotating material on a pedestal, an elevator car, and integrally rotated with the sheave shaft. The travel position of the flyweight and flyweight which is displaceable between the travel positions located radially outward of the governor sheave and is displaced from the normal position to the travel position by centrifugal force by the rotation of the governor sheave. Brake mechanism which is operated by displacement of and gives brake force to governor rope, adjustment lever which can rotate in the circumferential direction of governor sheave with respect to sheave shaft, and balance spring which presses fly weight in the direction counter to centrifugal force by rotation of governor sheave Has, between the fly weight and the adjusting lever And a linkage mechanism for interlocking the operation member and the adjustment lever with each other, the adjustment lever being attached to the sheave shaft and displaced in the axial direction of the sheave shaft, wherein the adjustment lever is moved by displacement of the operation member in the axial direction of the sheave shaft. It is rotatable and adjustment of the distance with respect to the travel position of a normal position is performed by rotation of an adjustment lever.

BRIEF DESCRIPTION OF THE DRAWINGS It is a block diagram which shows the elevator apparatus by Embodiment 1 of this invention.

FIG. 2 is a front view illustrating the governor of FIG. 1. FIG.

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

FIG. 4 is a partial cross-sectional view showing a main part of the governor of FIG. 3.

Fig. 5 is an exploded perspective view showing the main part of the governor of Fig. 3.

FIG. 6 is a graph showing the relationship between the speed of the car, the first overspeed and the second overspeed, and the distance from the lowest end to the car in the normal operation of the elevator of FIG.

7 is a sectional view showing the principal parts of a governor of an elevator according to Embodiment 2 of the present invention.

FIG. 8 is a diagram showing the principal parts of a governor as viewed in the radial direction of the governor sheave of FIG. 7; FIG.

EMBODIMENT OF THE INVENTION Hereinafter, preferred embodiment of this invention is described with reference to drawings.

Embodiment 1.

BRIEF DESCRIPTION OF THE DRAWINGS It is a block diagram which shows the elevator apparatus by Embodiment 1 of this invention. In the figure, the drive device 2 is provided in the upper part of the hoistway 1. The main rope 3 is wound around the sheave 2a of the drive device 2. In the hoistway 1, the car 4 and the counterweight 5 are wound down by the main rope 3. In addition, a pair of cage guide rails 6 are provided in the hoistway 1 to guide the lifting and lowering of the cage 4, and a pair of counterweight guide rails (not shown) to guide the lifting and lowering of the counterweight 5. ) Is installed.

In the lower part of the cage | basket | car 4, the emergency stop device 7 for preventing the cage | basket | car 4 from falling is provided. The governor support member 8 is fixed to the upper part of the cage guide rail 6. On the governor support member 8, the governor 9 which detects the overspeed of the cage | basket | car 4 and operates the emergency stop device 7 is supported.

In the vicinity of the bottom of the hoistway 1, a tension pulley 10 of rotating material is provided. The governor rope 11 is wound around the governor 9 and the tension pulley 10. One end and the other end of the governor rope 11 are connected to the emergency stop device 7 via the lever 12. The governor rope 11 is cyclically moved with the lifting and lowering of the car 4.

FIG. 2 is a front view of the governor 9 of FIG. 1. In the figure, the pedestal 13 is fixed on the governor support member 8. Horizontally extending sheave shaft 14 is supported by pedestal 13 with a rotating material. The governor sheave 15 is fixed to the sheave shaft 14 by which the governor rope 11 is wound. The governor sheave 15 is rotated integrally with the sheave shaft 14.

A side of the governor sheave 15 is provided with a pair of flyweights 17 that can be rotated around the pin 16. Each fly weight 17 is displaceable between the normal position and the travel position located radially outward of the governor sheave 15 from the normal position by the rotation around the pin 16. Each fly weight 17 is rotated from a normal position to a travel position by centrifugal force by the rotation of the governor sheave 15. Each fly weight 17 is connected to each other by a link 18.

An operation hook 19 is fixed to one end of one fly weight 17. The operation hook 19 is a diameter of the governor sheave 15 by rotating from the normal position of the fly weight 17 to the travel position. Direction is displaced outward.

The pedestal 13 is equipped with 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. The car stop switch 20 has a switch main body 21 and a switch lever 22 provided on the switch main body 21 and operated by an operation hook 19. The switch lever 22 is operated by the operating hook 19 when the fly weight 17 is rotated to the stop operating position located between the normal position and the travel position. In addition, when the speed of the cage | basket | car 4 reached the 1st overspeed (normally about 1.3 times the rated speed), the flyweight 17 rotates to a stop operation position, and the speed | rate of the cage | basket | car 4 is 2nd. When the overspeed (usually about 1.4 times the rated speed) is reached, it is rotated to the travel position.

The governor sheave 15 is provided with a travel lever 24 which can be rotated about a shaft 23 parallel to the pin 16. A part of the travel lever 24 is in contact with one fly weight 17. The travel lever 24 is rotated about the shaft 23 by the rotation of the fly weight 17. The shaft 23 is provided with a torsion spring (not shown) which presses the travel lever 24 in the direction to be brought into contact with the fly weight 17.

The pedestal 13 is provided with a ratchet 25 rotatable about the sheave shaft 14. The ratchet 25 is adapted to rotate about the sheave shaft 14. A plurality of teeth is provided on the outer peripheral portion of the ratchet 25.

One of the pins 16 is rotatably provided with an engaging hook 26 that selectively engages with either the travel lever 24 or the ratchet 25. The engagement hook 26 is pressurized in the direction to be engaged with the ratchet 25 by the tension spring which is not shown in figure. The engagement hook 26 is disengaged from the ratchet 25 in engagement with the travel lever 24 when the flyweight 17 is in its normal position. In addition, when the fly weight 17 is rotated to the travel position, the engagement hook 26 is disengaged from the engagement with the travel lever 24 and is rotated by the spring force of the tension spring to engage the ratchet 25.

Moreover, the arm 27 is attached to the base 13 by the rotation material. On the arm 27, a shoe 28 pressurized to the governor sheave 15 through the governor rope 11 is mounted as a rotating material. A spring shaft 29 is displaced through the tip portion 27a of the arm 27 so as to be displaceable. At one end of the spring shaft 29, a connection link 30 connected to the ratchet 25 by a rotating material is fixed. A spring bearing member 31 is provided at the other end of the spring shaft 29. Between the tip portion 27a of the arm 27 and the spring bearing member 31, a spring 32 for pressing the shoe 28 against the governor rope 11 is provided.

The ratchet 25 is rotated in the same direction as the governor sheave 15 by the engagement of the engaging hook 26 at the time of rotation of the governor sheave 15. As a result, the arm 27 is rotated in the direction in which the shoe 28 is pressed against the governor sheave 15. Movement of the governor rope 11 is braked by the shoe 28 being pressed against the governor sheave 15 via the governor rope 11.

In addition, the braking mechanism 33 for applying the braking force to the governor rope 11 includes the travel lever 24, the ratchet 25, the engagement hook 26, the arm 27, the shoe 28, and the spring shaft 29. ), A connecting link 30, a spring bearing member 31, and a pressure spring 32.

3 is a rear view of the governor 9 of FIG. 2. In the figure, the sheave shaft 14 is provided with an adjustment lever 34 which can rotate in the circumferential direction of the governor sheave 15 with respect to the sheave shaft 14. The adjustment lever 34 is installed on the outer periphery of the lever body 35 including the cylindrical portion 35a through which the sheave shaft 14 passes, and extends in the circumferential direction of the governor sheave 15. It has the rotation control part 37 provided with the one long hole 36, and the lever piece 38 provided in the outer peripheral part of the lever main body 35, and extending to the radially outer side of the lever main body 35. As shown in FIG.

The pin 39 passed through the long hole 36 is fixed to the side surface of the governor sheave 15. The pin 39 is slidable in the long hole 36 in the longitudinal direction of the long hole 36. The rotation control part 37 slides with respect to the pin 39 by rotation with respect to the sheave shaft 14 of the adjustment lever 34. 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 main body 35. The connecting body 40 which connects the fly weight 17 and the adjustment lever 34 is connected between the other end part of one fly weight 17 and the lever piece 38. As shown in FIG. The linking body 40 is provided with an elastic telescopic rod 41 connected between the fly weight 17 and the lever piece 38, and a telescopic rod 41, which is opposed to the centrifugal force due to the rotation of the governor sheave 15. It has the balance spring 42 which presses the fly weight 17 in the direction to be made.

The fly weight 17 and the adjustment lever 34 are interlocked with each other by the connecting body 40. Therefore, the normal position of the fly weight 17 can be adjusted in the direction approaching or away from the travel position by the rotation of the adjustment lever 34. That is, the rotation angle (rotation distance) of the fly weight 17 from the normal position to the travel position is adjustable by the adjustment lever 34. As a result, the magnitudes of the first and second overspeeds for emergency stopping the car 4 can be adjusted by the rotation of the adjustment lever 34.

4 is a partial cross-sectional view showing the main portion of the governor 9 of FIG. 5 is an exploded perspective view showing the main portion of the governor 9 in FIG. 3. The sheave shaft 14 is provided with the operation member 43 which can be displaced in the axial direction of the sheave shaft 14. The operation member 43 has a pipe portion 44 surrounding the sheave shaft 14 and a plate-shaped disk portion 45 provided at an outer circumferential portion of the pipe portion 44. The disk part 45 is arrange | positioned perpendicular to the axis line in the sheave shaft 14.

An interlock mechanism 46 for interlocking the operation member 43 and the adjustment lever 34 is provided between the sheave shaft 14 and the lever main body 35. The interlock mechanism 46 converts the displacement with respect to the sheave shaft 14 of the operation member 43 to the rotation with respect to the sheave shaft 14 of the adjustment lever 34.

The interlock mechanism 46 is a displacement body 47 integrated with the operation member 43, and a displacement body when the displacement body 47 is displaced with respect to the sheave shaft 14 and is provided on the outer circumferential surface of the sheave shaft 14. A sheave shaft side spline portion 48, which is a first guide portion for rotating the 47 to the sheave shaft 14, and an inner circumferential surface of the cylindrical portion 35a, so that the displacement body 47 is provided with the sheave shaft 14; Has a lever side spline 49 which rotates the cylindrical portion 35a with respect to the displacement body 47 in a direction opposite to the rotational direction of the displacement body 47 by the sheave shaft side spline portion 48 when displaced with respect to. have.

An inner gear spline portion 50 fitted to the sheave shaft side spline portion 48 is provided on the inner circumferential surface of the displacement body 47, and an outer gear spline fit to the lever side spline portion 49 on the outer circumferential surface of the displacement body 47. The part 51 is provided. That is, the displacement body 47 is splined to each of the lever main body 35 and the sheave shaft 14. As a result, the displacement member 47 is displaceable while rotating in the axial direction of the sheave shaft 14 with respect to the sheave shaft 14 and the cylindrical portion 35a.

Tooth traces of the sheave shaft side spline portion 48 and the lever side spline portion 49 are 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 splined portions of inclined teeth. Moreover, the inclination direction (torsion direction) of the tooth trace of the sheave shaft side spline part 48 is reverse to the inclination direction (torsion direction) of the tooth trace of the lever side spline part 49. Further, the inclination angle (torsion angle) of the teeth traces of the sheave shaft side spline portion 48 is different from the inclination angle (torsion angle) of the teeth traces of the lever side spline portion 49.

When the displacement body 47 is displaced in the axial direction of the sheave shaft 14 with respect to the sheave shaft 14, the displacement body 47 rotates with respect to the sheave shaft 14 and the displacement body of the cylindrical portion 35a ( The rotation for 47 is carried out simultaneously. The rotation direction with respect to the sheave shaft 14 of the displacement body 47 and the rotation direction with respect to the displacement body 47 of the cylindrical part 35a are mutually reversed. Accordingly, the adjustment lever 34 has a rotation angle with respect to the sheave shaft 14 of the displacement body 47 and the displacement of the cylindrical portion 35a when the displacement body 47 is displaced in the axial direction of the sheave shaft 14. It rotates with respect to the sheave shaft 14 by the angular difference of the rotation angle with respect to a sieve.

The pedestal 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 which contacts the disk portion 45 and displaces the operation member 43. Moreover, an encoder (not shown) which is a detection unit for detecting the position and the speed of the car 4 is provided in the sheave shaft 14. The encoder generates a signal corresponding to the rotation of the governor sheave 15, and sends the generated signal to an elevator controller (not shown). The elevator control device controls the actuator device based on the information from the encoder.

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 in the normal operation of the elevator of FIG. In the drawing, the elevator 4 has a constant speed between the acceleration and deceleration section in which the car 4 is accelerated and decelerated in the vicinity of the lowermost floor and the uppermost floor (one end and the other end floor). There is a constant speed section moving to.

The elevator control apparatus includes a normal speed pattern 55 which is a speed of the car 4 during normal operation, a first overspeed pattern 56 that is larger than the normal speed pattern 55, and a first overspeed The 2nd overspeed pattern 57 which becomes a value larger than the pattern 56 is set corresponding to the position of the cage | basket | car 4, respectively.

The normal speed pattern 55, the first overspeed pattern 56, and the second overspeed pattern 57 are set so as to be continuously reduced toward the terminal layer in the acceleration / deceleration section so as to be a constant value in the constant speed section. .

The elevator controller is configured to control the actuator device such that the magnitude of each of the first and second overspeeds is adjusted in accordance with the first and second overspeed patterns 56 and 57. That is, the elevator controller is configured to accelerate and decelerate. As the position of the car 4 approaches the lowermost floor or the uppermost floor in the section, the actuator device is controlled so that the size of each of the first and second overspeeds is continuously reduced.

In this example, the elevator control device is such that the rotation distance between the normal position and the travel position of the flyweight 17 becomes smaller when the car 4 is moved in the direction in which the car 4 is closer to the lowermost floor or the uppermost floor within the acceleration / deceleration section. The actuator device is controlled to displace the operation member 43 in the direction. In addition, the elevator control device operates the member in a direction in which the rotational distance between the normal position and the travel position of the flyweight 17 increases when the car 4 moves away from the lowermost floor or the uppermost floor in the acceleration / deceleration section. The actuator device is controlled to displace the 43.

Next, the operation will be described. In the elevator control apparatus, the speed of the cage | basket | car 4 is always requested | required based on the information from an encoder. When the car 4 is moving in the constant speed section, the operation member 43 is not displaced by the actuator device, but is fixed at a predetermined position. Therefore, the magnitude | size of each of the 1st and 2nd overspeed is made constant regardless of the position of the cage | basket | car 4.

When the car 4 is moving 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 fly weight 17 is displaced outward in the radial direction of the governor sheave 15 so that the position of the car 4 is closer to the lowermost floor or the uppermost floor, and the position of the car 4 is The distance from the lowermost layer or the uppermost layer is adjusted so as to be displaced radially inward of the governor sheave 15.

That is, the magnitude | size of each of the 1st and 2nd overspeeds becomes continuously small so that the cage | basket | car 4 may approach the lowest floor or the uppermost floor, and it continuously increases as it moves away from the lowest floor or the uppermost floor.

In normal operation, the car 4 is moved in the hoistway 1 in accordance with the normal speed pattern 55. At this time, the flyweight 17 is rotated to the radially outer side of the governor sheave 15 by the centrifugal force by the rotation of the governor sheave 15 corresponding to the speed of the car 4.

For some reason, when the speed of the car 4 further rises and the speed of the car 4 reaches the value of the 1st overspeed pattern 56, the flyweight 17 rotates to a stop operation position. And the switch lever 22 is operated by the operating hook 19. As a result, the supply of electricity to the drive device 2 is stopped by the control of the elevator control device, the brake device is operated to stop the car 4.

For example, even if the drive device 2 stops, such as when the main rope 3 breaks, the car 4 is moved without stopping, and the speed of the car 4 is two overspeed patterns 57. ), The flyweight 17 is further rotated by the centrifugal force by the rotation of the governor sheave 15 to reach the travel position. As a result, the meshing ring 26 is engaged with the travel lever 24 so that the meshing ring 26 is engaged with the ratchet 25. As a result, the ratchet 25 is only rotated in the rotational direction of the governor sheave 15.

The rotational force of the ratchet 25 is transmitted to the arm 27 via the connecting link 30, the spring shaft 29, the spring bearing member 31 and the pressure spring 32. As a result, the arm 27 is rotated, and the shoe 28 is pressed against the governor rope 11 by the pressure spring 32 after the shoe 28 contacts the governor rope 11. As a result, the governor rope 11 is braked.

When the movement of the governor rope 11 is stopped, the car 4 is moved and continues, so that the lever 12 is operated and the emergency stop device 7 operates.

In such an elevator governor 9, the adjustment lever 34 which can be rotated in the circumferential direction of the governor sheave 15 and the operation member 43 which can be displaced in the axial direction of the sheave shaft 14 operate the linkage mechanism 46. Since the fly weight 17 is rotated by the rotation of the adjustment lever 34, even if the governor sheave 15 is being rotated, the operation member 43 is moved to the sheave shaft 14. By displacing in the axial direction of, the rotation angle from the normal position of the fly weight 17 to the travel position can be adjusted, and the magnitude of the first and second overspeeds can be easily matched to the position of the car 4. Can be changed.

As a result, in the acceleration / deceleration section provided near the terminal layer, the magnitudes of the first and second overspeeds can be reduced toward the terminal layer. In the constant speed section provided between the respective acceleration and deceleration sections, the first and second overspeeds The magnitude of the degree can be made constant. Therefore, in the vicinity of the terminal layer, the first and second overspeeds can be made smaller than the constant speed section, and the braking distance at the time of emergency stop of the car 4 can be shortened. Thereby, the shock absorber provided in the pit part of the hoistway 1 can be miniaturized, and the depth dimension of a pit part can be made small. In addition, it is possible to reduce the size of the overhead for allowing the car 4 to pass or jump. That is, the dimension of the height direction of the hoistway 1 can be reduced.

Moreover, when the interlock mechanism 46 is provided in the displacement body 47 integrated with the operation member 43, and the outer peripheral surface of the sheave shaft 14, and the displacement body 47 is displaced with respect to the sheave shaft 14, And the sheave shaft side spline portion 48 that rotates the displacement body 47 with respect to the sheave shaft 14 and the inner circumferential surface of the cylindrical portion 35a of the adjustment lever 34 so that the displacement body 47 is moved to the sheave shaft 14. Lever side spline part 49 which rotates the cylindrical part 35a with respect to the displacement body 47 in the reverse direction to the rotation direction of the displacement body 47 by the sheave shaft side spline part 48 when it displaces with respect to Therefore, since the sheave shaft side spline portion 48 and the lever side spline portion 49 are able to generate a predetermined resistance against the displacement of the displacement body 47 in the axial direction of the sheave shaft 14, the governor Position shift with respect to the sheave shaft 14 of the displacement body 47 can be prevented by the centrifugal force or the vibration by the rotation of the sheave 15.

Moreover, the displacement body 47 is splined with respect to the sheave shaft 14 by the sheave side spline part 48 which inclined the tooth trace with respect to the axial direction of the sheave shaft 14, and the tooth trace is a sheave shaft 14 Is splined to the cylindrical portion 35a by the lever side spline portion 49 inclined with respect to the axial direction of the axial direction, so that the displacement body is displaced by the displacement of the displacement body 47 in the axial direction of the sheave shaft 14. (47) can be rotated with respect to the sheave shaft 14 more reliably, and the cylindrical part 35a can be rotated with respect to the displacement body 47 more reliably.

In the above example, although the coupling to the cylindrical portion 35a and the sheave shaft 14 of the displacement body 47 is splined together, displacement of the displacement body 47 in the axial direction of the sheave shaft 14 is achieved. If it is a coupling | bonding which can rotate the displacement body 47 by this, it does not need to be limited to a spline coupling.

Embodiment 2.

7 is a sectional view showing the principal parts of the elevator governor according to Embodiment 2 of the present invention. 8 is a principal part configuration diagram which shows the governor 9 of what looked along the radial direction of the governor sheave 15 of 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 1st projection part 61a which protruded from the inner peripheral surface of the displacement body 47, and a 2nd projection part 61b which protruded from the outer peripheral surface of the displacement body 47. As shown in FIG.

The outer circumferential surface of the sheave shaft 14 is provided with a sheave shaft side groove portion 62 in which the first protrusion 61a is slidably inserted. The sheave shaft side groove 62 is inclined along 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. As a result, the displacement member 47 is displaced in the axial direction of the sheave shaft 14 while being rotated with respect to the sheave shaft 14.

On the inner circumferential surface of the cylindrical portion 35a, a lever side groove portion 63 in which the second protrusion 61b is slidably inserted is provided. The lever side groove portion 63 is inclined with respect to the axial direction of the sheave shaft 14 in the reverse direction of the inclination direction of the sheave shaft side groove portion 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 part 35a is rotated with respect to the displacement body 47 by the displacement of the sheave shaft 14 to the axial direction in the opposite direction to the rotational direction of the displacement body 47 by the sheave shaft side groove part 62.

The inclination angle of the sheave shaft side groove portion 62 with respect to the axial direction of the sheave shaft 14 is different from the inclination angle of the lever side groove portion 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 with respect to the sheave shaft 14, the displacement body 47 rotates with respect to the sheave shaft 14 and the displacement body of the cylindrical portion 35a ( The rotation for 47 is carried out simultaneously. The rotation direction with respect to the sheave shaft 14 of the displacement body 47 and the rotation direction with respect to the displacement body 47 of the cylindrical part 35a are mutually opposite. Therefore, the adjustment lever 34 is the rotation angle with respect to the sheave shaft 14 of the displacement body 47 and the displacement of the cylindrical part 35a when the displacement body 47 is displaced in the axial direction of the sheave shaft 14. It is rotated with respect to the sheave shaft 14 and the regulator sheave 15 by the angle difference with the rotation angle with respect to the sieve.

In addition, the interlock mechanism 64 for interlocking the operation member 43 and the adjustment lever 34 with each other, the displacement body 47, the slide pin 61, the sheave shaft side groove portion 62 and the lever side groove portion 63 Have. The other configuration is the same as that in the first embodiment.

In such an elevator apparatus, the sheave shaft side groove portion 62 which rotates the displacement body 47 with respect to the sheave shaft 14 by guiding the first protrusion 61a protruding from the inner circumferential surface of the displacement body 47 is a sheave. The lever side groove part 63 provided in the shaft 14 and which rotates the cylindrical part 35a with respect to the displacement body 47 by guiding the 2nd protrusion part 61b which protrudes from the outer peripheral surface of the displacement body 47 Is provided on the inner circumferential surface of the cylindrical portion 35a, the configuration of the interlock mechanism 64 can be simplified, and the manufacturing cost can be reduced.

In addition, although the sheave shaft side groove part 62 is provided in the sheave shaft 14 in the said example, a long hole may be sufficient as the sheave shaft side groove part 62. In addition, although the lever side groove part 63 is provided in the cylindrical part 35a in the said example, you may make the lever side groove part 63 into a long hole.

Thus, the elevator apparatus which concerns on this invention is useful for being able to easily adjust the setting overspeed for making an emergency stop of a car.

Claims (4)

Sheave shaft supported on the base by rotating material, A governor sheave which is wound with the governor rope moving together with the car and rotates integrally with the sheave shaft, It is provided in the governor sheave, and between the normal position and the travel position located radially outward of the governor sheave than the normal position can be displaced with respect to the governor sheave, the normal by the centrifugal force by the rotation of the governor sheave A fly weight displaced from the position to the travel position, A braking mechanism operated by the displacement of the fly weight to the travel position to impart a braking force to the governor rope, An adjustment lever rotatable in the circumferential direction of the governor sheave with respect to the sheave shaft; A coupling body having an equilibrium spring for urging the flyweight in a direction against the centrifugal force and connected between the flyweight and the adjustment lever, An operation member provided on the sheave shaft and displaceable in the axial direction of the sheave shaft, and an interlock mechanism for interlocking the operation member and the adjustment lever with each other, The adjustment lever is rotatable by the displacement of the operation member in the axial direction of the sheave shaft, The adjustment of the distance with respect to the said travel position of the said normal position is performed by rotation of the said adjustment lever, The governor of an elevator characterized by the above-mentioned. The method of claim 1, The adjustment lever has a lever body including a cylindrical portion through which the sheave shaft passes, and a lever piece provided on the lever body and to which the connecting body is connected, The interlock mechanism includes a cyclically displaced body integrated with the operating member and a first rotating body of the displaced body with respect to the sheave shaft when the displaced body is displaced with respect to the sheave shaft and provided on an outer circumferential surface of the sheave shaft. The cylindrical portion is rotated with respect to the displacement body in a direction opposite to the rotation direction of the displacement body by the first guide portion when the guide portion and the inner peripheral surface of the cylindrical portion are disposed and the displacement body is displaced with respect to the sheave shaft. An elevator governor having a second guide portion. The method of claim 2, At least one of the first guide portion and the second guide portion is a spline portion in which a tooth trace is inclined with respect to the axial direction of the sheave axis, The displacer is splined to at least one of the cylindrical portion and the sheave shaft by the spline portion. The method of claim 2, 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 speed governor of the elevator, characterized in that the displacement body is provided with a projection inserted into the groove.

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