JP6868681B1 - Elevator emergency stop device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an elevator emergency stop device which can be used for a guide rail having a variation in friction coefficient without increasing the number of parts. An emergency stop device for an elevator is provided with a leaf spring whose ends are arranged so as to be inclined with respect to the longitudinal direction of a guide rail of the elevator, and a leaf spring which is pulled up so as to advance to the guide rail. A movable wedge that is pressed, a guide wedge that receives a pushing force from the leaf spring and presses the movable wedge against the guide rail, and a load receiving plate that is provided above the movable wedge and receives the pulled up movable wedge. The end portion of the load receiving plate is provided in close non-contact with the upper end portion of the leaf spring. [Selection diagram] Fig. 2

Description

Embodiments of the present invention relate to an elevator emergency stop device.

The elevator is equipped with an emergency stop device that forcibly stops the car when, for example, the car descends at a speed exceeding the rated speed. The emergency stop device has a pair of movable wedges arranged so as to sandwich the guide rail, and brake shoes are attached to the surfaces of the movable wedges facing the guide rails.

When the descending speed of the car exceeds the rated speed, the governor device is activated, and the movable wedge of the emergency stop device is pulled up along the guide rail via the safety link mechanism interlocked with the governor device. As a result, the movable wedge advances toward the guide rail, and the brake shoe is pressed against the guide rail. As a result, a braking force based on friction is generated between the brake shoe and the guide rail, and the car stops urgently.

Japanese Unexamined Patent Publication No. 2018-100146 Japanese Patent No. 2001-192184 Japanese Patent No. 2726604

Conventionally, the braking force of the emergency stop device of an elevator largely depends on the friction coefficient of the guide rail, and when a new guide rail is used, the friction coefficient is confirmed by a drop test or the like. Then, when the friction coefficient of the guide rail varies widely, there is a problem that the elevator emergency stop device cannot be used. Further, when trying to overcome the problem, there are problems that it is complicated, the number of parts is large, and the cost is increased.

An object to be solved by the present invention is to provide an elevator emergency stop device that can be used for a guide rail having a variation in friction coefficient without increasing the number of parts.

In order to solve the above problems, the emergency stop device for the elevator of the embodiment is pulled up so as to advance to the guide rail and a leaf spring whose end is inclined with respect to the longitudinal direction of the guide rail of the elevator. A movable wedge that is pressed against the guide rail, a guide wedge that receives a pushing force from the leaf spring and presses the movable wedge against the guide rail, and a movable wedge that is provided above the movable wedge and is pulled up. A load receiving plate is provided, and the end portion of the load receiving plate is in close contact with the upper end portion of the leaf spring .

Front view of the elevator showing the positional relationship between the governor device and the emergency stop device. The front view of the emergency stop device which concerns on embodiment in a normal state. The plan view which shows the relative positional relationship between a guide rail and an emergency stop device. An enlarged view of the emergency stop device according to the embodiment. The front view at the time of braking of the emergency stop device which concerns on embodiment. An enlarged view of the emergency stop device according to the embodiment during normal operation and braking. The correlation diagram of the load receiving plate and the leaf spring of the non-road stop device according to the embodiment.

Hereinafter, embodiments will be described with reference to the drawings. In the following description, the functions and components which are substantially or substantially the same are designated by the same reference numerals and will be described as necessary.

(First Embodiment)
FIG. 1 shows a front view of an elevator showing the positional relationship between the governor device and the emergency stop device. As shown in FIG. 1, the elevator 1 has a hoistway 3 provided in the building 2. The car 4 and the balance weight 5 are arranged in the hoistway 3. The car 4 and the balance weight 5 are examples of the elevating body, respectively. The car 4 is movably supported by the hoistway 3 via a pair of first guide rails 6 fixed to the hoistway 3. The balance weight 5 is movably supported by the hoistway 3 via a pair of second guide rails 7 (only one of which is shown) fixed to the hoistway 3.

The first guide rail 6 and the second guide rail 7 extend in a straight line along the height direction of the hoistway 3, and are arranged in parallel with each other in the hoistway 3 at intervals. There is. Further, the first guide rail 6 and the second guide rail 7 each include a leg portion 8 and a blade portion 9. The blade portion 9 projects from the central portion of the surface of the leg portion 8 so as to be orthogonal to the leg portion 8.

As shown in FIG. 1, the car 4 includes a car frame 11 and a car body 12. The car frame 11 has a lower beam 13, an upper beam 14, and left and right vertical rails 15a and 15b. The lower beam 13 passes under the car body 12 and straddles between the lower ends of the vertical rails 15a and 15b. The upper beam 14 passes over the car body 12 and straddles between the upper ends of the vertical rails 15a and 15b. The vertical rails 15a and 15b are respectively located immediately before the first guide rail 6 and stand up along the first guide rail 6.

The car body 12 is a square box-shaped element and is supported by the car frame 11. The car body 12 is surrounded by the lower beam 13, the upper beam 14, and the vertical bars 15a and 15b of the car frame 11.

The lower guide devices 17a and 17b are attached to the left end and the right end of the lower beam 13. Similarly, the upper guide devices 18a and 18b are attached to the left end portion and the right end portion of the upper beam 14. The lower guide devices 17a and 17b and the upper guide devices 18a and 18b each have a plurality of rollers. The roller rolls and contacts the blade portion 9 of the first guide rail 6 from three sides to guide the car 4 so as to be able to move up and down along the first guide rail 6.

The hoisting machine 20 is installed in the machine room 22 at the upper end of the hoistway 3. The hoisting machine 20 suspends the car 4 and the balance weight 5 on the hoistway 3 via the main rope 23. By hoisting the main rope 23 or operating the hoisting machine 20 in the unwinding direction, the car 4 and the balance weight 5 are driven in a slidable manner along the hoistway 3.

As shown in FIG. 1, the elevator 1 is a safety device that forcibly stops the elevating body when the elevating body such as the car 4 and the balance weight 5 descends at a speed exceeding a predetermined rated speed. Equipped with 25. The safety device 25 includes a governor device 26 and a pair of emergency stop devices 27a and 27b. The safety device 25 can be applied to both the car 4 and the balance weight 5, but in the present embodiment, the safety device 25 applied to the car 4 will be described.

The governor device 26 includes a governor sheave 30 having a pair of fly weights, a ratchet wheel 31, a rope grip 32, a tensioner sheave 33, a governor rope 34, and a governor switch 35 as main elements.

The governor sheave 30, ratchet wheel 31, rope grip 32 and governor switch 35 are housed in the machine room 22 together with the hoist 20. The tensioner sheave 33 is installed at the bottom of the hoistway 3. The governor rope 34 is wound endlessly between the governor sheave 30 and the tensioner sheave 33. Therefore, the governor rope 34 extends in the vertical direction along the hoistway 3 so as to cover the entire range in which the car 4 moves up and down.

The governor rope 34 has an intermediate portion between the governor sheave 30 and the tensioner sheave 33 connected to the safety link mechanism 36. The safety link mechanism 36 includes a pair of upright lift levers 37a and 37b. The lift levers 37a and 37b are individually connected to a pair of emergency stop devices 27a and 27b provided in the car 4.

As a result, the governor rope 34 travels at the same speed as the car 4 in the direction in which the car 4 moves up and down.

The rope grip 32 has a fixed shoe 38 and a movable shoe 39. The fixed shoe 38 faces the governor rope 34 that is extended downward from the governor sheave 30 in the machine room 22. The movable shoe 39 is located on the opposite side of the fixed shoe 38 with the governor rope 34 in between. Further, the movable shoe 39 is rotatable between a first position retracted to the upper side of the fixed shoe 38 and a second position in which the governor rope 34 is sandwiched in cooperation with the fixed shoe 38.

In the first position, the movable shoe 39 is separated from the governor rope 34 and is hooked on the ratchet wheel 31. Therefore, the movable shoe 39 is held in the first position as long as the descending speed of the car 4 does not exceed the rated speed.

Further, the governor switch 35 shuts off the power supply of the hoisting machine 20 and activates the electromagnetic brake of the hoisting machine 20 in a state where the descending speed of the car 4 exceeds the rated speed.

Although FIG. 1 illustrates an elevator with a machine room, the present embodiment may be applied to an elevator without a machine room (machine room-less elevator). In this case, the hoisting machine 20 is installed on a beam installed at the upper part of the hoistway 3.

As shown in FIG. 1, the emergency stop devices 27a and 27b are attached to the lower beam 13 of the car frame 11 so as to be located immediately before the first guide rail 6. Since the emergency stop devices 27a and 27b have a common configuration with each other, one of the emergency stop devices 27a will be used for description.

FIG. 2 is a normal front view of the emergency stop device according to the embodiment. The emergency stop device 27a includes a device main body 41, guide wedges 42a and 42b, a leaf spring 43, a pair of movable wedges 60a and 60b, and a load receiving plate 61.

FIG. 3 is a plan view showing the relative positional relationship between the guide rail and the emergency stop device. The apparatus main body 41 includes an upper end plate 46, a lower end plate 47, and a pillar 48. The upper end plate 46 is a plate on a square shape and is fixed to the lower surface of the lower beam 13 of the car frame 11. The lower end plate 47 is a plate on a square having substantially the same size as the upper end plate 46, and is located below the upper end plate 46. The pillar 48 is interposed between the upper end plate 46 and the lower end plate 47 so as to integrally connect the upper end plate 46 and the lower end plate 47. Therefore, the upper end plate 46 and the lower end plate 47 are arranged in parallel with each other at intervals in the height direction of the hoistway 3.

A recess into which the blade portion 9 of the first guide rail 6 enters is formed in the central portion of the front end of the upper end plate 46. Similarly, a recess is formed in the central portion of the front end of the lower end plate 47 so as to avoid the blade portion 9 of the first guide rail 6.

The pair of guide wedges 42a and 42b are arranged between both front end plates of the upper end plate 46 and both front end plates of the lower end plate 47. The guide wedges 42a and 42b are arranged so as to face each other with the blade portion 9 of the first guide rail 6 sandwiched between them, and are supported by the device main body 41 so as to move toward and away from the blade portion 9, respectively. ing.

The guide wedges 42a and 42b each have a guide surface 52 and a spring receiving portion 53. The guide surface 52 is formed so as to face the side surface of the blade portion 9 of the first guide rail 6. The guide surface 52 is inclined so as to approach the side surface of the blade portion 9 as it advances from the lower end to the upper end of the guide wedges 42a and 42b.

The spring receiving portion 53 is formed on the outer portion of the guide wedges 42a and 42b so as to be located on the opposite side of the guide surface 52. The spring receiving portion 53 is provided so as to face the leaf spring 43 in the inclined direction.

As shown in FIG. 3, the leaf spring 43 is curved in a substantially U shape. According to this embodiment, initial pressure is applied to the leaf spring 43 so as to urge both ends of the leaf spring 43 in a direction approaching each other.

The end of the leaf spring 43 is fitted to the guide wedges 42a and 42b. Further, a pair of pressing tools 55a and 55b are attached to both ends, respectively.

As shown in FIG. 2, the leaf spring 43 has a pressing surface 54. The pressing surface 54 is provided so as to face the spring receiving portion 53 of the guide wedges 42a and 42b. The pressing surface 54 is provided so as to be inclined with respect to the first first guide rail 6. The inclination angles of the leaf spring 43 and the pressing surface 54 are inclined by an angle θ1 with respect to the longitudinal direction of the guide rail 6, that is, the vertical direction (see FIG. 4 described later).

The upper end of the pressing surface 54 of the leaf spring 43 is close to the end of the load receiving plate 61. The load receiving plate 61 is provided above the guide wedges 42a and 42b. The load receiving plate 61 is provided below the upper end plate 46.

An elastic member (62) is provided between the load receiving plate 61 and the upper end plate 46. The elastic member includes, for example, a disc spring and a resin member. In the following example, a cushioning disc spring (disc spring 62) will be used as the elastic member. The upper end of the disc spring 62 is adhered to the lower surface of the upper end plate 46, and the other end is adhered to the upper surface of the load receiving plate 61. In FIG. 2, two disc springs 62 are provided on the left and right, but the number is not limited.

Elastic members (45a, 45b) are provided between the leaf spring 43 and the guide wedges 42a, 42b. The elastic member includes, for example, a disc spring and a resin member. In the following example, pressing disc springs (disc springs 45a and 45b) will be used as the elastic member. The ends of the disc springs 45a and 45b are adhered to the pressing surface 54 of the leaf spring 43, and the other ends are adhered to the spring receiving portions 53 of the guide wedges 42a and 42b.

The pressing force of the leaf spring 43 is urged to the guide wedges 42a and 42b via the disc springs 45a and 45b which are elastic members. In FIG. 2, two disc springs 45a and 45b are provided at the top and bottom, but the number is not limited.

FIG. 4 is an enlarged view of the region A surrounded by the alternate long and short dash line in the out-of-road stop device 27a of FIG. The load receiving plate 61 is provided in contact with the upper end portion of the guide wedge 42a. The right end of the load receiving plate 61 has an inclined surface 61a so as to face the inclination of the pressing surface 54 of the leaf spring 43. A gap V is formed between the right end of the load receiving plate 61 and the upper end of the leaf spring 43. That is, the load receiving plate 61 and the leaf spring 43 are normally provided in a non-contact manner. When the pressing surface 54 and the inclined surface 61a are parallel, the inclination angle of the inclined surface 61a is θ1 with respect to the vertical direction.

As shown in FIGS. 2 and 3, the movable wedges 60a and 60b are arranged so as to face each other with the blade portion 9 of the first guide rail 6 sandwiched between the guide wedges 42a and 42b. Since the movable wedges 60a and 60b have a common configuration with each other, one of the movable wedges 60a will be described.

The movable wedges 60a and 60b have base portions 44a and 44b and adjustment portions 49a and 49b, respectively. Adjusting portions 49a and 49b are provided on the tops of the base portions 44a and 44b. The adjusting portions 49a and 49b extend upward from the base portions 44a and 44b.

As an example, the adjusting portions 49a and 49b have a screw type mechanism, and the tops of the base portions 44a and 44b have screw holes so that the adjusting portions 49a and 49b rotate in the height direction of the adjusting portions 49a and 49b. The length can be adjusted. Thereby, the heights of the movable wedges 60a and 60b can be adjusted by the adjusting portions 49a and 49b.

Further, as an example, the adjusting portions 49a and 49b can adjust the length of the adjusting portions 49a and 49b in the height direction by sliding the upper end portions upward. Thereby, the heights of the movable wedges 60a and 60b can be adjusted by the adjusting portions 49a and 49b.

A roller unit 70 is interposed between the movable wedges 60a and 60b and the guide wedges 42a and 42b, respectively. The roller unit 70 includes a plurality of transfer rollers. The transfer roller is rotatably supported by the roller unit 70. The transfer rollers are arranged in a row in the longitudinal direction of the roller unit 70. The transfer roller is in contact with the guide surface 52 and the movable wedge 60a. The movable wedge 60a receives the urging force of the leaf spring 43 transmitted from the transfer roller.

In the case of the present embodiment, a linking rod (not shown) linked to the lift levers 37a and 37b (see FIG. 1) is connected to the lower ends of the movable wedges 60a and 60b.

Next, the operation of the safety device 25 will be described. In FIG. 1, when the car 4 moves up and down along the hoistway 3, the governor sheave 30 rotates via the governor rope 34, and the fly weight supported by the governor sheave 30 is displaced by centrifugal force.

When the descending speed of the car 4 exceeds the rated speed, the governor switch 35 is operated by the displaced fly weight. As a result, the power supply of the hoisting machine 20 is cut off, and the electromagnetic brake of the hoisting machine 20 is operated.

When the centrifugal force acting on the fly weight increases without stopping the car 4 despite the operation of the governor switch 35, the fly weight is caught on the ratchet wheel 31. As a result, the ratchet wheel 31 rotates following the governor sheave 30, and the movable shoe 39 of the rope grip 32 is disengaged from the ratchet wheel 31. Therefore, the movable shoe 39 rotates from the first position to the second position, and cooperates with the fixed shoe 38 to grab the governor rope 34.

As a result, the running of the governor rope 34 is stopped. Since the car 4 continues to descend even when the governor rope 34 is stopped, the lift levers 37a and 37b of the safety link mechanism 36 are pulled up with respect to the car 4.

The movements of the lift levers 37a and 37b are transmitted to the movable wedges 60a and 60b via the cooperation rod, and the movable wedges 60a and 60b are forcibly pulled up along the first guide rail 6.

FIG. 5 is a front view of the emergency stop device according to the embodiment when braking. The emergency stop device 27a at the time of braking will be described mainly using the configuration on the right side of FIG. 5 because the emergency stop device 27a has a symmetrical shape.

The leaf spring 43 applies a pushing force to the spring receiving portion 53 of the guide wedge 42a via the disc spring 45a in the direction of arrow α1 (see FIGS. 2 and 5).

The guide surface 52 of the guide wedges 42a and 42b in contact with the movable wedges 60a and 60b is inclined so as to approach the blade portion 9 of the first guide rail 6 as it advances upward. As shown in FIG. 5, when the movable wedges 60a and 60b are forcibly pulled up, they move toward the blade portion 9 of the first guide rail 6 while being guided by the transfer roller of the roller unit 70. By this movement, the brake shoes fixed to the movable wedges 60a and 60b are pressed against the blade portion 9 of the first guide rail 6.

The movable wedges 60a and 60b are elastically urged toward the first guide rail 6 by receiving the pushing force of the leaf spring 43, and the blade portion 9 of the first guide rail 6 is formed by the movable wedges 60a and 60b. It is firmly sandwiched between the brake shoes. Therefore, a braking force based on friction is generated between the brake shoe and the blade portion 9, and the car 4 makes an emergency stop.

When the movable wedges 60a and 60b sandwich the first guide rail 6, a pushing force is applied from the movable wedge 60a toward the guide wedge 42a in the direction of the arrow β1. The pushing force in the β1 direction becomes a repulsive force with respect to the pushing force in the α1 direction, and becomes a force for opening the guide wedges 42a and 42b in the outward direction.

When the car 4 makes an emergency stop, the movable wedges 60a and 60b may slide on the first guide rail 6 and reach the load receiving plate 61 depending on the friction coefficient of the guide rail 6. In this case, the upper ends of the movable wedges 60a and 60b push up the load receiving plate 61. When the load receiving plate 61 is pushed up, the disc spring 62 is contracted between the load receiving plate 61 and the upper end plate 46. At this time, a pushing force in the β2 direction is applied from the movable wedges 60a and 60b to the load receiving plate 61.

When a pushing force is applied from the movable wedges 60a and 60b to the load receiving plate 61, the disc spring 62 is compressed by pushing up the load receiving plate 61.

FIG. 6 is an enlarged view of the emergency stop device during normal operation and braking. FIG. 6A is a correlation diagram between the load receiving plate 61 and the leaf spring 43 during normal operation, and FIG. 6B is a correlation diagram between the load receiving plate 61 and the leaf spring 43 during braking.

In the normal case, as shown in FIG. 6A, a gap portion V is formed between the inclined surface 61a of the load receiving plate 61 and the pressing surface 54 of the leaf spring 43. When the load receiving plate 61 is pushed up during braking, as shown in FIG. 6B, the load receiving plate 61 is pushed up, so that the inclined surface 61a and the pressing surface 54 are in contact with each other, and the gap portion V disappears.

When the braking force is increased and the load receiving plate 61 is further pushed up, as shown in FIG. 5, the load receiving plate 61 moves the leaf spring 43 away from the blade portion 9 of the first guide rail 6 (arrow γ). Apply pushing force in the direction).

The greater the braking force and the greater the deceleration, the greater the braking force (arrow β1 in FIG. 5). A pushing force (arrow γ in FIG. 5) acts in the direction of expanding the leaf spring 43 by the load receiving plate 61. As a result, the force of the repulsive force with respect to the leaf spring 43 is dispersed in the arrow β1 and the arrow γ.

As a result, the repulsive force with respect to the leaf spring 43 is dispersed, and the leaf spring 43 is expanded. By expanding the leaf spring 43, the pushing force (spring force) applied to the guide wedges 42a and 42b and the movable wedges 60a and 60b can be reduced, and the braking force can be reduced. That is, the feedback of the pushing force works mechanically.

FIG. 7 is a correlation diagram between the load receiving plate 61 of the emergency stop device 27a and the leaf spring 43, and is an enlarged view of the vicinity of the gap V in FIG. The size of the gap V in FIG. 6A and the distance between the inclined surface 61a of the load receiving plate 61 and the pressing surface 54 of the leaf spring 43 are set based on the braking force and the spring constant of the disc spring 62. To. For example, the horizontal size of the gap V is x (m), the vertical size of the gap V is y (m), the pushing force of the load receiving plate 61 is F (N), and the spring constant is k. Assuming that the amount of contraction of the disc spring 62 in the height direction is y (m) and the inclination of the inclined surface 61a with respect to the horizontal direction is θ2,
F = ky ... Equation (1)
y = x · tan θ2 ... Equation (2)
It is represented by.

Further, when the pressing surface 54 and the inclined surface 61a are parallel, the inclination angles θ1 and θ2 are θ1 + θ2 = π / 2 ... Equation (3).
Will be.

The spring constant of the disc spring 62 may be changed, for example, depending on the characteristics of the elevator. For example, the spring constant may be changed according to the capacity of the car body 12. Further, the number of disc springs 62 may be increased or decreased according to the characteristics of the elevator.

The load receiving plate 61 elastically receives the push-up of the movable wedges 60a and 60b and applies a feedback force to the leaf spring 43. Therefore, the vertical magnitude y (m) of the gap portion V is a value calculated from the target braking force and the spring constant k of the disc spring 62, and a force that feeds back when the target braking force is exceeded is generated. Let me. The target braking force is a force corresponding to the deceleration of the elevator, and if the braking force is too large, sudden braking is applied. In order to prevent a sudden change in braking force, it is preferable that the pushing force generated by the disc spring 62 and the load receiving plate 61 back to the leaf spring 43 is smaller than the spring force generated by the spring constant of the leaf spring 43. is there. When the disc spring 62 is provided in parallel between the upper end plate 46 and the load receiving plate 61, it is set as the combined spring constant in the parallel arrangement.

When the leaf spring 43 is pushed by the load receiving plate 61, a pushing force is applied to the upper end portion of the leaf spring 43. Therefore, a twisting force is applied to the leaf spring 43 in the vertical direction. In order to suppress the unevenness of the pressing force applied to the guide wedges 42a and 42b, it is preferable that the spring constant of the disc springs 45a and 45b is smaller than the spring constant of the leaf spring 43. That is, the twisting distance of the upper end portion of the leaf spring 43 is smaller than the contracting length of the disc springs 45a and 45b. When the disc springs 45a and 45b are provided in parallel between the leaf spring 43 and the guide wedges 42a and 42b, the spring constant is a composite spring constant in the parallel arrangement.

As shown in FIGS. 2 and 5, the movable wedges 60a and 60b are provided with adjusting portions 49a and 49b above the base portions 44a and 44b. By adjusting the height with the adjusting portions 49a and 49b, the height of the movable wedges 60a and 60b can be adjusted according to the friction coefficient of the first guide rail 6. As a result, the emergency stop device 27a can be standardized regardless of the characteristics of the guide rail and the capacity and performance of the elevator.

Further, the structure may be such that the adjusting portions 49a and 49b are not provided. In this case, the bases 44a and 44b push up the load receiving plate 61.

In the above description of the embodiment, the first guide rail 6 has been used, but the same applies to the second guide rail 7. Further, in the above description of the embodiment, the emergency stop device 27a has been described, but the same applies to the emergency stop device 27b.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

1 ... elevator, 2 ... building, 3 ... hoistway, 4 ... car, 5 ... balance weight, 6 ... first guide rail, 7 ... second guide rail, 8 ... leg, 9 ... blade, 11 ... Basket frame, 12 ... Main body, 13 ... Lower beam, 14 ... Upper beam, 15a, 15b ... Vertical rail, 17a, 17b ... Lower guide device, 18a, 18b ... Upper guide device, 20 ... Hoisting machine, 22 ... Machine room, 23 ... main rope, 25 ... safety device, 26 ... governor device, 27a ... emergency stop device, 27b ... emergency stop device, 30 ... governor sheave, 31 ... ratchet wheel, 32 ... rope grip, 33 ... tensioner sheave, 34 ... governor rope, 35 ... governor switch, 36 ... safety link mechanism, 37a ... lift lever, 37b ... lift lever, 38 ... fixed shoe, 39 ... movable shoe, 41 ... device body, 42a, 42b ... guide wedge, 43 ... leaf spring , 44a, 44b ... base, 45a, 45b ... disc spring, 46 ... upper end plate, 47 ... lower end plate, 48 ... pillar, 49a, 49b ... adjustment part, 52 ... guide surface, 53 ... spring receiving part, 54 ... Pressing surface, 55a, 55b ... Pressing tool, 60a ... Movable wedge, 60a, 60b ... Movable wedge, 61 ... Load receiving plate, 61a ... Inclined surface, 62 ... Belleville spring, 70 ... Roller unit.

Claims (6)

A leaf spring whose ends are inclined with respect to the longitudinal direction of the elevator guide rail,
A movable wedge that is pulled up to advance into the guide rail and pressed against the guide rail,
A guide wedge that receives a pushing force from the leaf spring and presses the movable wedge against the guide rail.
A load receiving plate provided above the movable wedge and receiving the pulled up movable wedge,
Equipped with
The end of the load receiving plate is in close non-contact with the upper end of the leaf spring.
Elevator emergency stop device. When the movable wedge is pulled up, the load receiving plate is pressed by the movable wedge, the end of the load receiving plate comes into contact with the leaf spring, and a force for relaxing the pushing force is applied to the leaf spring. Add,
The elevator emergency stop device according to claim 1. The first elastic member provided on the load receiving plate and
A second elastic member provided between the leaf spring and the guide wedge,
The elevator emergency stop device according to claim 1 or 2. The first elastic member is a cushioning disc spring.
The emergency stop device for an elevator according to claim 3, wherein the pressing force generated by the cushioning disc spring and the load receiving plate on the leaf spring is a value smaller than the pressing force of the leaf spring. The second elastic member is a pressing disc spring.
The emergency stop device for an elevator according to claim 3, wherein the spring constant of the pressing disc spring is a value smaller than the spring constant of the leaf spring. The emergency stop device for an elevator according to claim 3, wherein the load receiving plate and the leaf spring come into contact with each other so as to obtain a target braking force in the gap between the load receiving plate and the leaf spring.

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