KR101928678B1 - Elevator apparatus - Google Patents

Abstract

In the elevator apparatus, the emergency stop device (15) is provided with an operation lever (16). The governor mechanism includes a governor sheave 18, a tension sheave 20 disposed at an interval in the vertical direction with respect to the governor sheave, a governor rope (not shown) wound on the governor sheave and tension sheave, 19). The inertia mass adding mechanism 101 adds an additional inertial mass to the governor mechanism when the car descends at least in the lower speed change section of the hoistway and releases the addition of the inertia mass when the car is lifted.

Description

[0001] ELEVATOR APPARATUS [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an elevator device for emergency stopping a car by an emergency stop device, for example, at the time of breakage of a suspension.

In the governor of the conventional elevator apparatus, the first overspeed velocity Vos (the operation speed of the operation stop switch) is set to about 1.3 times the rated speed Vo, and the second overspeed velocity Vtr (emergency stop operation speed) . For example, when it is detected that the car speed has exceeded the rated speed and reached the first excessive speed Vos due to an abnormality in the control device or the like, the power supply to the traction machine is cut off and the car is quickly stopped by the traction machine brake. Further, when it is detected that the car has fallen due to breakage of the main rope or the like and the car speed has reached the second excessive speed Vtr, the emergency stop device operates to stop the car in an emergency.

However, when the car reaches the bottom of the hoistway before the car speed reaches the first excessive speed Vos or the second overspeed speed Vtr, the car is decelerated to stop by the shock absorber. For this reason, a longer buffering stroke is required for the shock absorber as the speed to be decelerated is higher, and the length of the shock absorber is determined according to the first excessive speed Vos and the second excessive speed Vtr. Further, when the shock absorber becomes long, the depth of the feet of the hoistway becomes large.

On the other hand, in the conventional double-deck elevator, an inertial mass is added to the governor rope provided for the upper car and the lower car, which are movable in the car frame in the up-and-down direction opposite to each other. When the rope for driving the upper car or the lower car is broken, the emergency stop device is operated in response to the inertia force generated in accordance with the acceleration of the car drop (see, for example, Patent Document 1).

Further, in another conventional elevator apparatus, the emergency stop device operates by the large car acceleration caused by the rope rupture. In addition, the angle of the operating lever, the tension of the governor rope, and the rotational inertia mass of the governor mechanism are set so that the emergency stop device does not malfunction with a small acceleration (see, for example, Patent Document 2).

Japanese Patent Application Laid-Open No. H06-62124 Japanese Patent Application Laid-Open No. 1236374

In the conventional elevator apparatus as described above, there is still a possibility that the emergency stop device malfunctions due to vibration generated in the car, for example, in the case where power supply to the traction machine is interrupted by power failure or the like and the car is suddenly stopped by the traction machine brake. That is, when the braking force of the traction machine brake is set strongly, the vibration generated in the car by the operation of the emergency brake instantaneously approaches 1G, which is the gravitational acceleration. For this reason, the emergency stop device malfunctions due to the rotational inertia mass of the governor mechanism. Further, even when the car vibrates greatly due to the violent movement of the passenger in the car, there is a likelihood of malfunction of the emergency stop device.

An object of the present invention is to provide an elevator apparatus which can prevent a malfunction of an emergency stop device and save space in a hoistway by a simple structure.

The elevator apparatus according to the present invention is characterized in that the elevator apparatus according to the present invention is a elevator apparatus comprising an elevating device mounted on a car suspended from a car ascending and descending in a hoistway, a car suspended on the car, an emergency stop device mounted on the car, an operating lever for operating the emergency stopping device, A governor mechanism having a governor rope wound around a governor sheave and a tension sheave and connected to an operating lever, and a governor mechanism having a governor mechanism connected to the governor sheave, An inertia mass adding mechanism for adding an additional inertia mass to the governor mechanism when lowering the lower speed change section, which is an area from the lowest floor to the rated speed, and releasing the inertia mass at the time of raising the car Respectively.

The elevator apparatus according to the present invention is characterized in that the elevator apparatus according to the present invention is provided with an emergency stop device mounted on a car suspended from a car, a car suspended in a hoistway, an emergency stop device, an operation lever for operating the emergency stop device, A governor mechanism having a governor sheave wound on the governor sheave and the tension sheave and having a governor rope connected to the actuating lever, And a resistance adding mechanism that adds a resistance to the motion of the governor mechanism when the lower speed change section, which is an area until reaching the rated speed, is lowered and the resistance force is decreased or released when the car is lifted.

The elevator apparatus according to the present invention is characterized in that the elevator apparatus according to the present invention is provided with an emergency stop device mounted on a car suspended from a car, a car suspended in a hoistway, an emergency stop device, an operation lever for operating the emergency stop device, A governor mechanism having a governor rope wound on a governor sheave and a tension sheave and also connected to an operating lever, and a governor mechanism having a governor mechanism when the car descends the hoistway, And an inertia mass adding mechanism for adding an additional inertia mass to the mechanism and releasing the inertia mass when the car is lifted.

The elevator device of the present invention can reduce the space of the hoistway while preventing malfunction of the emergency stop device by a simple structure.

1 is a configuration diagram showing an elevator apparatus according to Embodiment 1 of the present invention;
Fig. 2 is a front view showing the relationship between the car guide rail and the emergency stop device of Fig. 1,
3 is a sectional view taken along the line III-III in Fig. 2,
Fig. 4 is a front view showing the operation of the emergency stop device of Fig. 1,
5 is a cross-sectional view taken along the line VV in Fig. 4,
Fig. 6 is an explanatory view showing the operation of the emergency stop device at the time of breakage of the suspension of Fig. 1; Fig.
Fig. 7 is an explanatory view showing a malfunction of the emergency stop device when the car is suddenly stopped by the traction machine brake of Fig. 1;
8 is a graph showing the relationship between the position of the operating lever of Fig. 7 and the pulling force of the operating lever,
Fig. 9 is an explanatory view showing the operation of the governor mechanism of the first embodiment when the car is lifted. Fig.
10 is an explanatory view showing the operation of the governor mechanism according to the first embodiment when the car is lowered;
11 is a front view showing details of the tension sheave of FIG. 9,
12 is an explanatory view showing an operation of the governor mechanism according to the modification of the first embodiment when the car is lifted.
13 is an explanatory view showing the operation of the governor mechanism according to the modification of the first embodiment when the car is lowered;
14 is a configuration diagram showing a main part of an elevator apparatus according to Embodiment 2 of the present invention,
Fig. 15 is a configuration diagram showing the governor mechanism and the additional mass of Fig. 14 when the car is lowered; Fig.
Fig. 16 is a configuration diagram showing the governor mechanism and the state of the additional mass body when the car rises from the state of Fig. 15;
17 is a configuration diagram showing the main part of an elevator apparatus according to Embodiment 3 of the present invention,
Fig. 18 is a configuration diagram showing the state of the governor mechanism and the damper mechanism of Fig. 17 when the car is lowered;
Fig. 19 is a diagram showing the state of the governor mechanism and the damper mechanism when the car rises from the state of Fig. 18;
Fig. 20 is a configuration diagram showing a main part of an elevator apparatus according to Embodiment 4 of the present invention,
Fig. 21 is a configuration diagram showing the state of the governor mechanism and the friction mechanism of Fig. 20 when the car is lowered;
Fig. 22 is a configuration diagram showing states of the governor mechanism and the friction mechanism when the car rises from the state of Fig. 21; Fig.
Fig. 23 is a plan view showing the friction mechanism of Fig. 20,
Fig. 24 is a sectional view taken along line XXIV-XXIV in Fig. 23,
Fig. 25 is a sectional view showing the state of the friction mechanism when the car is lowered from the state of Fig. 24,
26 is a sectional view showing the state of the friction mechanism when the car rises from the state of Fig. 25. Fig.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.

Embodiment 1

1 is a configuration diagram showing an elevator apparatus according to Embodiment 1 of the present invention. In the drawing, a machine room 2 is provided at an upper portion of the hoistway 1. The machine room 2 is provided with a traction machine (drive unit) 3, a deflection sheave 4 and a control unit 5. [ The traction machine 3 has a drive sheave 6, a traction machine motor for rotating the drive sheave 6 and a traction machine brake (electromagnetic brake) 7 for braking the rotation of the drive sheave 6. [

The traction machine brake 7 includes a brake wheel (drum or disk) coaxially coupled to the drive sheave 6, a brake shoe for braking the rotation of the brake wheel by abutting against the brake wheel, And an electronic magnet for releasing the braking force by releasing the brake shoe from the brake wheel in response to the brake spring.

The drive sheave (6) and the deflection sheave (4) are wound with a suspension body (8). As the suspension member 8, a plurality of ropes or a plurality of belts are used. A car (9) is connected to the first end of the suspension (8). The counterweight 10 is connected to the second end of the suspension member 8.

The car 9 and the counterweight 10 are suspended in the hoistway 1 by the suspension 8 and ascend and descend in the hoistway 1 by the driving force of the hoist 3. The control device 5 controls the rotation of the traction machine 3 to raise and lower the car 9 at the set speed.

A pair of car guide rails 11 for guiding the lift of the car 9 and a pair of counterweight guide rails 12 for guiding the lift of the counterweight 10 are installed in the hoistway 1 have. The bottom portion of the hoistway 1 is provided with a car shock absorber 13 for cushioning a collision with the bottom of the hoistway of the car 9 and a counterweight cushion 14 for buffering collision against the bottom of the hoistway of the counterweight 10 ).

In the lower portion of the car 9, an emergency stop device 15 for holding the car guide rail 11 to stop the car 9 is mounted. As the emergency stop device 15, a gradual emergency stop device is used (in general, a gradual emergency stop device is used in an elevator device having a rated speed exceeding 45 m / min).

The machine room 2 is provided with a governor 17 for detecting the overspeed running of the car 9. The governor 17 has a governor sheave 18, an overspeed detection switch, a rope catch, and the like. The governor sheave (18) is wound around the governor rope (19).

The governor rope 19 is annularly laid in the hoistway 1 and connected to the emergency stop device 15. [ Further, the governor rope 19 is wound around the tension sheave 20 disposed at the lower portion of the hoistway 1. When the car 9 ascends and descends, the governor rope 19 circulates and the governor sheave 18 rotates at a rotational speed corresponding to the running speed of the car 9.

In the governor 17, it is mechanically detected that the traveling speed of the car 9 has reached the excessive speed. In the governor 17, a first excessive speed Vos higher than the rated speed Vo and a second excessive speed Vtr higher than the first excessive speed are set as the excessive speed to be detected.

When the running speed of the car 9 reaches the first excessive speed Vos, the overspeed detection switch is operated. When the overspeed detection switch is operated, the power supply to the traction machine 3 is interrupted, and the traction machine brake 7 is actuated to suddenly stop the car 9. [

When the descending speed of the car 9 reaches the second excessive speed Vtr, the governor rope 19 is gripped by the rope catch, and the circulation of the governor rope 19 is stopped. When the circulation of the governor rope 19 is stopped, the operation lever 16 is operated, and the emergency stop device 15 is operated to cause the car 9 to stop in an emergency.

Fig. 2 is a front view showing the relationship between the car guide rail 11 and the emergency stop device 15 of Fig. 1, Fig. 3 is a sectional view taken along line III-III of Fig. 2, Fig. 4 is a front view of the emergency stop device 15, and Fig. 5 is a cross-sectional view taken along the line VV in Fig.

The emergency stop device (15) has a pair of left and right grip portions for gripping corresponding car guide rails (11). Each of the grip portions has a pair of wedges 25, a pair of wedge guides 26, and a plurality of wedge guide springs 27 as shown in Fig.

The wedge (25) is movable up and down with respect to the frame of the emergency stop device (15) along the inclined surface provided on the wedge guide (26). The wedge guide spring 27 is provided between the frame of the emergency stop device 15 and the wedge guide 26.

In the normal state, the wedge 25 faces the car guide rail 11 with a gap therebetween as shown in Fig. On the other hand, when the emergency stop device 15 is operated, the wedge 25 is lifted. At this time, the wedge 25 approaches the car guide rail 11 along the wedge guide 26, and eventually comes into contact with the car guide rail 11, as shown in Fig.

Then, when the wedge 25 is further lifted, the wedge 25 moves upward by pushing the wedge guide 26 in the horizontal direction so as to reduce the wedge guide spring 27. The pressing force acting on the car guide rail 11 from the wedge 25 is increased by the compression of the wedge guide spring 27 and the frictional force generated in the car guide rail 11 and the emergency stop device 15 is transmitted to the wedge (25). Thereby, the wedge 25 grasps the car guide rail 11, and the car 9 is brought to an emergency stop.

Fig. 6 is an explanatory view showing the operation of the emergency stop device 15 at the time of breakage of the suspension member 8 in Fig. The emergency stop device 15 is rotatably provided with an operation lever 16 (not shown in Fig. 1) for operating the emergency stop device 15. A wedge 25 is connected to the end of the operation lever 16. When the operating lever 16 is lifted (in the counterclockwise direction of FIG. 6), the wedge 25 is lifted in synchronization with the operating lever 16. That is, the emergency stop device 15 operates by rotating the operation lever 16 in the counterclockwise direction of Fig.

The emergency stop device 15 is provided with a rotation spring 22 for applying a force to the operation lever 16 in a direction opposite to the direction in which the emergency stop device 15 is operated (clockwise direction in Fig. 6). The rotation springs 22 are given an initial rotation amount. By this initial amount of rotation, a resistance force for lifting up the operating lever 16 is generated, and the operating lever 16 is prevented from being inadvertently rotated. Therefore, even when the hoist-machine brake 7 is actuated while the car 9 is running and the car 9 is vertically vibrated, the operating lever 16 is pulled up and the emergency stop device 15 is not operated.

A connecting portion 23 is fixed to the governor rope 19. A pull-up rod 24 is connected between the connecting portion 23 and the operating lever 16. That is, the governor rope 19 is connected to the emergency stop device 15 via the connecting portion 23, the pull-up bar 24 and the operation lever 16. [ The upper end of the lifting rod 24 is rotatably connected to the connecting portion 23. [ Further, the lower end of the lifting rod 24 is rotatably connected to the operating lever 16. [

The governor mechanism 100 of Embodiment 1 has a governor sheave 18, a governor rope 19, and a tension sheave 20. At the time of breakage of the suspension member 8, the car 9 falls downward at a gravitational acceleration of 1G. At this time, since the governor mechanism 100 is not affected by gravity, the speed is increased to aG lower than 1G (a &lt; 1.0). As a result, an acceleration difference occurs between the car 9 and the governor mechanism 100. Thereby, the speed of the governor mechanism 100 becomes kV (k <1) lower than the car speed V, and the operation lever 16 is pulled up, whereby the emergency stop device 15 is operated. Further, the car speed V at the time of operation of the emergency stop device 15 is lower than the rated speed Vo.

7 is an explanatory view showing a malfunction of the emergency stop device 15 when the car 9 is suddenly stopped by the traction machine brake 7 in Fig. When the traction machine brake 7 is operated during the lift of the car 9, the car 9 decelerates to about 0.3G. At this time, a downward acceleration is generated in the car 9. On the other hand, the governor mechanism 100 does not directly receive the braking deceleration force but decelerates to an acceleration bG lower than 0.3G (b <0.3). Therefore, the speed kV of the governor mechanism 100 is faster than the speed V of the car 9 (k> 1), and the emergency stop device 15 malfunctions due to the rise of the operation lever 16.

Here, FIG. 8 is a graph showing the relationship between the position of the operating lever 16 of FIG. 7 and the pulling force of the operating lever 16. When the emergency brake is operated, the spring force of the rotary spring 22 is stronger than the pulling force of the actuation lever 16 by F1, and the actuation lever 16 does not rise. On the other hand, when the suspension member 8 is broken, the pulling force is stronger than the spring force of the rotation spring 22 by F2, and the emergency stop device 15 is operated.

At this time, if the difference (F1 + F2) between the pulling force at the time of the emergency brake operation and the pulling force at the time of breakage of the suspension member 8 is small, the range of the spring force setting of the rotation spring 22 for preventing malfunction is limited. This makes it difficult to set, resulting in malfunction of the emergency stop device 15 or increase of the car speed due to delay of the operation time of the emergency stop device 15. [

In order to solve this problem, in Embodiment 1, a mechanism in which the rotational inertia mass of the governor mechanism 100 changes along the running direction is used. That is, at the time of lowering the car 9, the added mass rotates integrally with the tension sheave 20, thereby increasing the rotational inertia mass of the portion that moves integrally with the governor mechanism 100. On the other hand, when the car 9 is lifted, the additional mass is separated from the tension sheave 20 so that the added mass does not contribute to the inertia of the governor mechanism 100.

Fig. 9 is an explanatory view showing the operation of the governor mechanism 100 of the first embodiment when the car rises, Fig. 10 is an explanatory view showing the operation of the governor mechanism 100 of the first embodiment when the car is lowered, 9 is a front view showing the details of the tension sheave 20 of FIG. On the same axis of rotation as the tension sheave 20, a rotary disk 28 is provided. The tension sheave (20) and the rotary disk (28) are connected by a rotary shaft (29).

The rotary shaft 29 is directly connected to the rotary disk 28. The rotary shaft 29 is connected to the tension sheave 20 via the ratchet mechanism 30 shown in Fig. The ratchet mechanism (30) has a ratchet (31), a plurality of claws (32), and a plurality of springs (33). The ratchet 31 is fixed to the rotary shaft 29 and rotates integrally with the rotary shaft 29. [ A plurality of teeth 31a are provided on the outer periphery of the ratchet 31. [

Each claw 32 is rotatably supported by a tension sheave 20. The spring 33 is provided between the tension sheave 20 and the claw 32 and presses the claw 32 against the outer periphery of the ratchet 31. [

11, the claw 32 slides on the outer periphery of the ratchet 31 and rotates integrally with the tension sheave 20 when the tension sheave 20 is rotated clockwise in Fig. Therefore, the ratchet 31 does not rotate, and the rotating shaft 29 does not rotate either.

When the tension sheave 20 rotates counterclockwise in Fig. 11, the claw 32 enters the teeth 31a during the downward movement of the car, and the ratchet 31 rotates together with the tension sheave 20 . Thus, the rotary shaft 29 and the rotary master 28 rotate integrally with the tension sheave 20. As described above, the ratchet mechanism 30 does not transmit the rotation of the tension sheave 20 when the car 9 is lifted to the rotation master 28, and the rotation of the tension sheave 20 when the car 9 is lowered To the rotation disc 28. [

The inertia mass adding mechanism 101 according to the first embodiment has a rotary disk 28, a rotary shaft 29 and a ratchet mechanism 30. The inertia mass adding mechanism 101 has a structure in which the inertia mass And releases the addition of the inertia mass when the car 9 is lifted.

In this way, when the car 9 descends, the tension inert sheave 20 and the rotary disk 28 integrally rotate, and thus the rotational inertia mass of the governor mechanism 100 increases as compared to when the car rises . Therefore, the movement of the governor mechanism 100 is delayed with respect to the movement of the car 9 when the car is lowered, while the speed of the car 9 is increased without delay of the governor mechanism 100 when the car is lifted. It becomes easy to follow the movement.

Therefore, at the time of collapse of the suspension member 8 at the time of descending the car, the acceleration difference between the governor mechanism 100 and the car 9 becomes large and the emergency stop device 15 can be immediately operated, The acceleration difference between the governor mechanism 100 and the car 9 is reduced in the emergency brake operation of the emergency stop device 15 (or up and down movement by the play of the passenger), and the erroneous operation of the emergency stop device 15 can be more reliably prevented . In this way, the emergency stop device 15 can be prevented from malfunctioning and the space of the hoistway 1 can be saved by a simple structure.

Further, the setting range of the rotation spring 22 for preventing malfunction of the emergency stop device 15 can be greatly widened, so that the adjustment operation is facilitated and the restraint of the passenger due to the malfunction can be more reliably prevented .

Since the rotation shaft 29 and the rotary disk 28 are connected to the tension sheave 20 via the ratchet mechanism 30, the governor mechanism 100 can be changed greatly.

In the case where it is difficult to sufficiently increase the rotational inertia mass only by the rotary disk 28 due to the dimensional limitation of the rotary disk 28, as shown in Figs. 12 and 13, the inertia mass adding mechanism 101, It is possible to easily increase the rotational inertia of the governor mechanism 100 by adding the additional disk 34 which is a separate disk of rotation from the rotary disk 28 and the loop-shaped rope 35 as the carrier. The rope 35 is wound on the rotating disc 28 and the additional disc 34 and transfers the rotation of the rotating disc 28 to the additional disc 34. [

In the first embodiment, the rotary disk 28 is connected to the tension sheave 20 via the ratchet mechanism 30. However, it may be connected to the governor sheave 18. [

Embodiment 2

Next, Fig. 14 is a configuration diagram showing the main part of the elevator apparatus according to Embodiment 2 of the present invention. The additional mass body 41 as the inertia mass adding mechanism is provided in the lower speed change section in the hoistway 1 instead of the rotary disk 28, the rotary shaft 29 and the ratchet mechanism 30 of the first embodiment, That is, in the region from the lowermost layer to the rated speed. A first contact member 38 is provided on the connecting portion 23 connecting the operating lever 16 and the governor mechanism 100.

The additional mass body 41 includes a lower rotating disc 21 adjacent to the tension sheave 20, an upper rotating disc 36 disposed directly above the lower rotating disc 21, A second contact member 39 fixed to the rope 37 at one side of the lower rotating disc 21 and a second contact member 39 fixed to the other side of the lower rotating disc 21 as the rope 37 And a return weight (40) fixed to the first and second arms (37, 37).

The first contact member 38 strikes the second contact member 39 when the car 9 is lowered to the lower speed change section. The mass of the weight 40 is set to a value slightly heavier than the second contact member 39. [ The other configuration is the same as that of the first embodiment.

14, when the car 9 is located near the uppermost layer, the first contact member 38 is away from the second contact member 39. As shown in Fig. In this state, the weight 40 is separated from the lower rotating disk 40 by the difference in mass between the second contact member 39 and the returning weight 40 in a state in which the first contact member 38 is away from the second contact member 39. [ (21), and the second contact member (39) is close to the upper rotation disc (36).

15, when the car 9 descends and reaches the lower speed change section, the first contact member 38 contacts the second contact member 39, and the governor mechanism 100 and the additional mass member (41) move integrally. Thereby, when the car 9 descends in the lower speed change section, an additional rotational inertia mass is added to the governor mechanism 100. [

16, when the car 9 is lifted from the lower speed change section, the first contact member 38 moves away from the second contact member 39. As shown in Fig. At this time, in a state in which the second contact member 39 is away from the first contact member 38, the second contact member 39 (the second contact member 39) is moved at an acceleration determined by the mass difference between the return member 40 and the second contact member 39 ).

Therefore, if the mass of the weight 40 is set so that the rising acceleration of the second contact member 39 is small, the second contact member 39 is raised at a velocity sufficiently lower than the rising velocity of the car 9. Thereby, as shown in Fig. 16, the first contact member 38 is moved away from the second contact member 39. Therefore, when the car 9 is lifted, the additional mass body 41 is separated from the governor mechanism 100, and the addition of the inertial mass by the additional mass body 41 is released.

In such an elevator apparatus, only when the car 9 descends in the lower speed change section, the rotational inertia mass of the portion that moves integrally with the governor mechanism 100 increases. Therefore, when the suspension member 8 is broken in the lower speed change section, the acceleration difference between the car 9 and the governor mechanism 100 becomes large, and the emergency stop device 15 immediately operates.

On the other hand, when the car 9 is lower than the lower speed change section and when the car 9 is lifted, since the rotational inertia mass of the governor mechanism 100 remains small, The acceleration difference of the governor mechanism 100 is unlikely to occur. Therefore, it is possible to more reliably prevent the emergency stop device 15 from malfunctioning during the emergency brake operation, in a wider range of car positions. In this way, the emergency stop device 15 can be prevented from malfunctioning and the space of the hoistway 1 can be saved by a simple structure.

Embodiment 3

Next, Fig. 17 is a configuration diagram showing the main part of the elevator apparatus according to Embodiment 3 of the present invention. In the third embodiment, instead of the additional mass 41 of the second embodiment, a damper mechanism 42 as a resistance adding mechanism is provided in the lower speed change section in the hoistway 1. [

The damper mechanism 42 has a plunger 43, a cylinder 44, a return spring 45, an oil 46, and a second contact member 47. The plunger 43 is inserted into the cylinder 44 so as to be vertically movable. The return spring 45 is interposed between the bottom of the cylinder 44 and the lower end of the plunger 43 and pushes the plunger 43 upward. The inside of the cylinder 44 is filled with the oil 46. At the lower end of the plunger 43, an orifice is provided.

The second contact member 47 is fixed to the upper end of the plunger 43. The first contact member 38 strikes the second contact member 47 when the car 9 is lowered to the lower speed change section. As the material of the second contact member 47, for example, rubber is used. As a result, the collision sound and vibration when the first contact member 38 contacts the second contact member 47 are alleviated. Other configurations are the same as those of the first and second embodiments.

17, when the car 9 is located near the uppermost layer, the first contact member 38 is away from the second contact member 47. As shown in Fig. The plunger 43 is protruded from the cylinder 44 by the maximum amount by the restoring force of the return spring 45 and the second plunger 43 protrudes from the second contact member 47 in the state where the first contact member 38 is away from the second contact member 47, The contact member 47 is located above the cylinder 44.

18, when the car 9 descends and reaches the lower speed change section, the first contact member 38 contacts the second contact member 47, and the governor mechanism 100 and the plunger 43 move integrally. At this time, the governor mechanism 100 receives the fluid resistance force (damping force) from the oil 46 in the cylinder 44 by the orifice at the lower end of the plunger 43. That is, the plunger 43 descends while applying a resistance force to the governor mechanism 100 when the car 9 descends in the lower speed change section.

As a result, the inertial force of the governor mechanism 100 does not change, but the damping force generated in the governor mechanism 100 increases. Therefore, when the car 9 descends in the lower speed change section, A large acceleration difference is generated between the car 9 and the governor mechanism 100 and the emergency stop device 15 immediately operates to prevent the car 9 from dropping safely at a low speed.

19, when the car 9 is lifted from the lower speed change section, the first contact member 38 moves away from the second contact member 47. As shown in Fig. At this time, when the second contact member 47 is away from the first contact member 38, the plunger 43 and the second contact member 47 are raised by the restoring force of the return spring 45.

However, the rising speed of the plunger 43 and the second contact member 47 is slower than the rising speed of the connecting portion 23 due to the fluid resistance of the oil 46 of the plunger 43. Thereby, as shown in Fig. 19, the first contact member 38 is moved away from the second contact member 47. That is, the plunger 43 is separated from the governor mechanism 100 when the car 9 is lifted.

Therefore, even if the emergency brake is operated while the car 9 is moving up, the difference in acceleration between the car 9 and the governor mechanism 100 is small, so that the emergency stop device 15 can be prevented from malfunctioning. In this way, the emergency stop device 15 can be prevented from malfunctioning and the space of the hoistway 1 can be saved by a simple structure.

Further, only when the car 9 descends in the lower speed change section, the damping force generated in the governor mechanism 100 is increased, so that the area in which the emergency stop device 15 malfunctions can be greatly reduced.

The rising speed of the plunger 43 can be adjusted by the orifice area at the lower end of the plunger 43, the spring force of the return spring 45, and the viscosity of the oil 46.

In the second and third embodiments, the first contact member 38 directly contacts the additional mass body 41 or the damper mechanism 42. However, a magnet may be provided on the contact surface to repel each other. As a result, the collision sound due to the contact can be eliminated, and the passenger in the car is not discomforted.

Embodiment 4

Next, Fig. 20 is a configuration diagram showing the main part of the elevator apparatus according to Embodiment 4 of the present invention. In the fourth embodiment, instead of the additional mass body 41 of the second embodiment, a friction guide rail 49 is provided in the lower speed change section in the hoistway 1. [ The friction guide rail (49) is disposed parallel to the car guide rail (11).

In the fourth embodiment, a wedge mechanism 48 is provided in the connecting portion 23 instead of the first contact member 38 in the second embodiment. The resistive force applying mechanism of the fourth embodiment is a friction mechanism 60 having a friction guide rail 49 and a wedge mechanism 48. Fig. 21 is a structural view showing the state of the governor mechanism 100 and the friction mechanism 60 in the downward movement of the car in Fig. 20, and Fig. 22 is a view showing the governor mechanism 100 and the friction mechanism 60 shown in Fig.

Next, Fig. 23 is a plan view showing the friction mechanism 60 of Fig. 20, and Fig. 24 is a sectional view along line XXIV-XXIV of Fig. The width of the upper end of the friction guide rail 49 gradually decreases toward the upper end. The wedge mechanism 48 includes a pair of friction wedges 50, a plurality of friction wedge springs 51, a pair of guide members 52, a plurality of horizontal springs 53, ).

The friction wedge 50 is arranged so as to place the friction guide rail 49 from both sides when the car 9 is positioned in the lower speed change section. The friction wedge spring (51) is interposed between the lower end of the friction wedge (50) and the frame body (54). The friction wedge 50 is movable up and down by the expansion and contraction of the wedge spring 51.

Each guide member 52 is provided with an inclined surface for guiding the corresponding friction wedge 50. The horizontal directional spring 53 is interposed between the guide member 52 and the frame member 54. The guide member 52 is movable in the horizontal direction by the expansion and contraction of the horizontal directional spring 53. Other configurations are the same as those of the first to third embodiments.

25, when the wedge mechanism 48 passes through the friction guide rail 49 by the descent of the car 9, the friction wedge 50 comes into contact with the friction guide rail 49, (Resistive force).

When the friction wedge 50 is subjected to an upward force, the guide member 52 moves in the horizontal direction to compress the horizontal directional spring 53. Therefore, the compressive force of the horizontal directional spring 53 increases the force of the friction wedge 50 pressing the friction guide rail 49, and the frictional force generated in the friction wedge 50 is further increased.

As described above, when the car 9 is lowered in the lower speed change section, the wedge mechanism 48 slides on the friction guide rail 49 to receive a large frictional force, and the governor mechanism 100 moves upward . Therefore, when the suspension member 8 is broken when the car 9 descends in the lower speed change section, a delay occurs in the movement of the governor mechanism 100 relative to the fall of the car 9, The emergency stop device 15 immediately operates due to the difference in acceleration between the accelerator pedal 9 and the governor mechanism 100. [

On the other hand, as shown in Fig. 26, when the car 9 is lifted, the friction wedge 50 is subjected to downward frictional force. As a result, the guide member 52 moves in the direction approaching the friction guide rail 49, and the pressing force on the friction wedge 50 by the horizontal direction spring 53 is lowered, thereby reducing the frictional force. Therefore, at the time of raising the car, the frictional force generated in the governor mechanism 100 becomes smaller than that at the time of descending the car, and the difference in acceleration between the car 9 and the governor mechanism 100 is small, (15) can be prevented from malfunctioning. In this way, the emergency stop device 15 can be prevented from malfunctioning and the space of the hoistway 1 can be saved by a simple structure.

Further, only when the car 9 descends in the lower speed change section, the frictional force generated in the governor mechanism 100 is increased, so that the area in which the emergency stop device 15 malfunctions can be greatly reduced.

Although the elevator apparatus of 1: 1 roping is shown in Fig. 1, the present invention is also applicable to an elevator apparatus of 2: 1 roping, for example.

Further, the present invention can be applied to various types of elevator apparatuses other than a machine room-free elevator without the machine room 2. [

1: hoistway, 8: suspension, 9: car, 15: emergency stop, 16: operation lever, 18: governor sheave, 19: governor rope, 20: tension sheave, 21: 35: rope (conveyor), 36: upper rotating disk, 37: rope (conveyor), 41: additional mass (inertial mass adding mechanism), 42: damper mechanism The friction stir welding apparatus according to any one of claims 1 to 3, wherein the friction member is a frictional wedge.

Claims (8)

A car that moves up and down the hoistway,
The cargo hanging body,
An emergency stop device mounted on the car,
An operating lever provided on the emergency stop device for operating the emergency stop device,
A governor sheave which is wound around the governor sheave and the tension sheave, and a tension sheave which is disposed at an interval in the vertical direction with respect to the governor sheave; and a governor rope A governor mechanism having
Further adding an inertia mass to the governor mechanism when lowering the lower speed change section, which is an area from when the car reaches at least the lowest speed of the hoistway to the rated speed, and releasing addition of the inertia mass when the car is lifted And an inertia mass adding mechanism
Elevator device. The method according to claim 1,
Wherein the inertia mass adding mechanism has a rotating disk and a ratchet mechanism provided between the governor sheave or the tension sheave and the rotating disk,
The ratchet mechanism transmits the motion of the governor mechanism only to the rotating disk when the car descends, and rotates the rotating disk
Elevator device. 3. The method of claim 2,
The inertia mass adding mechanism may further include an additional disk which is a rotation disk separate from the rotation disk, and a loop-shaped carrier which is wound on the rotation disk and the additional disk and transmits the rotation of the disk to the additional disk With
Elevator device. The method according to claim 1,
Wherein the inertia mass adding mechanism is an additional mass having a lower rotating disc, an upper rotating disc disposed immediately above the lower rotating disc, and a loop-shaped carrier wound around the lower rotating disc and the upper rotating disc,
Wherein the additional mass moves integrally with the governor mechanism when the car descends the lower speed change section and is separated from the governor mechanism when the car is lifted
Elevator device. A car that ascends and descends in the hoistway,
The cargo hanging body,
An emergency stop device mounted on the car,
An operating lever provided on the emergency stop device for operating the emergency stop device,
A governor mechanism having a governor sheave wound on the governor sheave and the tension sheave and a governor rope connected to the operating lever;
A resistance force is applied to the motion of the governor mechanism when the car descends a lower speed change section which is an area from at least the lowest layer of the hoistway to a rated speed, Having an attachment mechanism
Elevator device. 6. The method of claim 5,
Wherein the resistance adding mechanism is a damper mechanism having a spring-supported plunger,
Wherein the plunger is lowered while applying a resistance force to the governor mechanism when the car is lowered in the lower speed change section and is separated from the governor mechanism when the car is lifted
Elevator device. 6. The method of claim 5,
Wherein the resistance applying mechanism is a friction mechanism having a friction guide rail provided in the lower speed change section in the hoistway and a wedge mechanism provided at a connecting portion between the governor rope and the operation lever,
Wherein the wedge mechanism comprises:
And a frictional wedge receiving frictional force by contact with the friction guide rail,
The frictional force received by the friction wedge is made smaller when the car rises above the lower speed change section than the frictional force received by the friction wedge when the car descends the lower speed change section
Elevator device. delete

Images