WO2017013737A1

WO2017013737A1 - Elevator device

Info

Publication number: WO2017013737A1
Application number: PCT/JP2015/070698
Authority: WO
Inventors: 研一中橋
Original assignee: 三菱電機株式会社
Priority date: 2015-07-21
Filing date: 2015-07-21
Publication date: 2017-01-26
Also published as: CN107848760B; JPWO2017013737A1; JP6494760B2; CN107848760A

Abstract

This elevator device is equipped with: a hoisting machine (4) equipped with a sheave (5), a motor, and a brake; a rope (3) which connects a car (1) and a weight (2), and is wound around the sheave (5); a deflector sheave (6) which is provided between the sheave (5) and the weight (2), and around which the rope (3) is wound; a deflector sheave mounting beam (7) which supports the deflector sheave (6) and allows the vertical movement of the deflector sheave (6); and a spring (10) which controls the vertical position of the deflector sheave (6) according to the value of in-car load in the car (1). The spring (10) causes the deflector sheave (6) to move downward in response to an increase in the in-car load, and causes the deflector sheave (6) to move upward in response to a decrease in the in-car load.

Description

Elevator equipment

The present invention relates to an elevator apparatus, and more particularly to an elevator apparatus that reduces a shock by controlling a deceleration at an emergency stop according to a load in a car.

A conventional elevator machine hoist includes a sheave, a deflector, a motor for rotating the sheave, and a brake for braking the rotation of the sheave. A rope is wound around the sheave and the deflector. A basket is connected to one end of the rope. A weight is connected to the other end of the rope. The basket and the weight are moved up and down in the hoistway by a motor. Further, when the cage arrives, the rotation of the sheave is braked by the brake, and the cage stops.

Also, an emergency stop is provided on the lower side of the basket. In the event of an emergency, the emergency stop engages with a guide rail provided in the hoistway to prevent the car from moving up and down. The emergency stop is only used if the rope breaks and if for some reason the car begins to descend at a speed exceeding the rated speed. Therefore, even in an emergency stop such as an earthquake, the cage is usually stopped by the brake of the hoisting machine.

When the conventional elevator system is completed, a hoisting machine brake test is conducted. Based on the result of the test, the brake torque is adjusted as necessary.

Also, an emergency stop test will be conducted when the conventional elevator system is completed. In the test, the emergency stop is operated with the cage stopped, and the motor is driven in the direction in which the cage descends. At this time, since the raising / lowering of the basket is prevented by the emergency stop, the basket does not move. As a result, the rope loosens, and as a result, the sheave begins to idle. On the other hand, if the stopping force of the emergency stop is insufficient, the rope does not loosen and the cage descends. From this, it can be determined that the emergency stop is good if the cage does not descend.

Since the emergency stop test is performed as described above, at the time of the test, the hoist motor needs to generate a very large torque sufficient for the sheave to start spinning. The capacity of the hoisting machine motor is determined by the magnitude of this torque.

However, the magnitude of this torque is larger than the torque required for actual operation. Therefore, if the capacity of the motor of the hoisting machine can be determined based on the torque required for actual operation, the capacity of the motor can be reduced.

Therefore, in Patent Document 1, a movable device for moving the position of the deflecting wheel is provided. The movable device raises the position of the deflecting wheel above the position during normal operation during the emergency stop test. Thereby, the winding angle of the rope around the sheave is reduced. As a result, the traction of the rope can be reduced. Thereby, the torque used for the emergency stop test can be reduced. As a result, the capacity of the motor can be reduced.

JP 2002-348073 A

In Patent Document 1, the position of the deflector is changed only when a test at the time of completion is performed. After the test is completed, the position of the deflector is returned to the original position. Therefore, in patent document 1, the position of a deflecting vehicle cannot be changed during operation of an elevator.

As described above, during normal operation, the basket is stopped by the brake of the hoisting machine. In addition, even in an emergency stop such as an earthquake, the basket is stopped by the hoisting machine brake. The brake torque required for stopping varies depending on the load in the car.

However, in conventional elevator equipment, the brake torque is adjusted at the time of completion. Therefore, the brake torque is always constant. In the conventional elevator apparatus, the brake torque cannot be changed according to the load fluctuation in the car. Also in the above-mentioned Patent Document 1, the brake torque is always constant.

通常 When a normal basket is landed, the basket stops based on a preset stop speed pattern. Therefore, if an appropriate stop speed pattern is selected, the passenger is not shocked even if the brake torque is constant.

However, during an emergency stop, the car is stopped with a stop speed pattern that is faster than the normal stop speed pattern. At this time, if the brake torque is constant, an unnecessarily large deceleration occurs when the load in the cage is small. As a result, the basket suddenly stopped, and the passengers were shocked by the basket.

The present invention has been made to solve such a problem, and it is an object of the present invention to obtain an elevator apparatus that can control the deceleration according to the load in the car and reduce the impact when the car stops. It is aimed.

This invention connects a hoisting machine including a sheave, a motor that rotates the sheave, and a brake that brakes the sheave, a basket and a weight, and is wound around the sheave. A sled wheel provided between a rope, the sheave, and the weight, the sled wheel wound with the rope, and the sled wheel that supports the sled wheel and allows the sled wheel to move in a vertical direction. A mounting beam, and a position control unit that controls a vertical position of the deflector according to a value of the load in the cage of the cage, the position control unit according to an increase in the load in the cage It is an elevator apparatus which moves a baffle downward and moves the baffle upward according to the reduction | decrease of the load in the said basket.

In the present invention, the position control unit moves the deflecting vehicle downward in accordance with an increase in the load in the cage and moves the deflecting vehicle upward in accordance with a decrease in the load in the cage. Thereby, since the traction of the rope can be changed, the deceleration at the time of stopping the car can be controlled to reduce the impact at the time of stopping the car.

It is a block diagram which shows the structure of the elevator apparatus which concerns on Embodiment 1 of this invention. It is a partial front view which shows the structure of the elevator apparatus which concerns on Embodiment 1 of this invention. It is a partial side view which shows the structure of the elevator apparatus which concerns on Embodiment 1 of this invention. It is a partial front view which shows the structure of the elevator apparatus which concerns on Embodiment 1 of this invention. It is a partial side view which shows the structure of the elevator apparatus which concerns on Embodiment 1 of this invention. It is a block diagram which shows the structure of the elevator apparatus which concerns on Embodiment 2 of this invention. It is a partial front view which shows the structure of the elevator apparatus which concerns on Embodiment 2 of this invention. It is a partial side view which shows the structure of the elevator apparatus which concerns on Embodiment 2 of this invention. It is a partial front view which shows the structure of the elevator apparatus which concerns on Embodiment 2 of this invention. It is a partial side view which shows the structure of the elevator apparatus which concerns on Embodiment 2 of this invention. It is explanatory drawing which showed in a graph the relationship between the cage deceleration in a common elevator apparatus, and the load factor in a cage. It is explanatory drawing explaining the principle of the automatic adjustment of the vertical direction position of the deflector wheel by the spring which concerns on Embodiment 1 of this invention.

¡The brake torque required to stop the car changes according to the load value in the car. However, in the conventional elevator apparatus, since the brake torque is adjusted during the test at the time of completion, the brake torque is always constant. Therefore, in the conventional elevator apparatus, a large deceleration occurs when the car is brought to an emergency stop with a small load in the car. Therefore, in the elevator apparatus according to the present invention, a mechanism is provided that can automatically adjust the vertical position of the deflector according to the load variation in the car. As a result, the traction of the rope is controlled, and the impact when the car stops is mitigated.

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

Embodiment 1 FIG.
1 is a schematic configuration diagram showing a configuration of an elevator apparatus according to Embodiment 1 of the present invention. As shown in FIG. 1, a basket 1 and a weight 2 are provided in a hoistway. A hoisting machine 4 is provided at the upper part of the hoistway. The hoist 4 raises and lowers the basket 1 and the weight 2. The hoisting machine 4 has a hoisting machine main body and a sheave 5. The hoisting machine main body includes a motor and a brake. The sheave 5 is rotated by a motor. A plurality of ropes 3 are wound around the sheave 5. Further, a deflecting wheel 6 is disposed between the sheave 5 and the weight 2. The rope 3 is also wound around the deflector 6. A basket 1 is connected to one end of the rope 3. A weight 2 is connected to the other end of the rope 3. The basket 1 and the weight 2 are suspended in a hoistway by a rope 3. The cage 1 and the weight 2 are moved up and down in the hoistway 1 by the rotation of the sheave 5.

Further, the hoisting machine 4 is mounted on the hoisting machine base 8. The hoisting machine base 8 is fixed to the upper part of the hoistway. The hoisting machine base 8 is provided with a deflecting wheel mounting beam 7 for mounting the deflecting wheel 6. The deflecting wheel mounting beam 7 supports the deflecting wheel 6. The deflecting wheel mounting beam 7 enables the deflecting wheel 6 to move in the vertical direction. The deflector wheel mounting beam 7 has a rectangular shape. The longitudinal direction of the deflector wheel mounting beam 7 is the vertical direction, that is, the ascending / descending direction. The hoisting machine base 8 is also rectangular. The longitudinal direction of the hoisting machine base 8 is the horizontal direction. Therefore, the vertical length of the hoisting machine base 8 is shorter than the vertical direction of the deflector wheel mounting beam 7. The baffle mounting beam 7 is provided with a vertical adjustment groove 9 for moving the baffle 6 in the vertical direction. The vertical adjustment groove 9 extends in the vertical direction, that is, in the up-and-down direction. A central shaft 61 of the deflector wheel 6 is inserted into the vertical adjustment groove 9. The central shaft 61 of the baffle wheel 6 is guided by the vertical adjustment groove 9 and can move in the vertical direction. In this way, the deflector wheel mounting beam 7 supports the deflector wheel 6 and moves the deflector wheel 6 in the vertical direction.

2A, 2B, 3A, and 3B are partial detailed views of the elevator apparatus according to the present embodiment. 2A and 2B show a case where the load in the car is small, and FIGS. 3A and 3B show a case where the load in the car is large. 2A is a front view, and FIG. 2B is a side view corresponding to FIG. 2A. Similarly, FIG. 3A is a front view, and FIG. 3B is a side view corresponding to FIG. 3A.

2A, 2B, 3A, and 3B, a pair of baffle mounting beams 7 and a pair of hoisting machine bases 8 are provided. As shown in FIGS. 2B and 3, the two hoisting machine bases 8 are provided back to back. A baffle mounting beam 7 is provided between the two hoisting machine bases 8. The baffle mounting beam 7 is also provided back to back. Each hoisting machine base 8 supports each baffle mounting beam 7. Between the two deflector wheel mounting beams 7, a deflector wheel 7 is arranged. As shown in FIGS. 2B and 3B, the upper end 71 and the lower end 72 of each baffle mounting beam 7 are bent at right angles in the same direction. Therefore, as shown in FIGS. 2B and 3B, the shape of the side surface of each baffle mounting beam 7 is a U-shape. Similarly, the upper end 81 and the lower end 82 of each hoisting machine base 8 are bent at right angles in the same direction. Accordingly, the shape of the side surface of each hoisting machine base 8 is a U-shape as shown in FIGS. 2B and 3B. The upper end 71 of each baffle mounting beam 7 is disposed on the upper end 81 of each hoisting machine base 8. The lower surface of the upper end 71 of each baffle mounting beam 7 and the upper surface of the upper end 81 of each hoisting machine base 8 are joined. The vertical length of each baffle mounting beam 7 is longer than the vertical length of each hoisting machine base 8. Therefore, the lower end 72 of each deflector wheel mounting beam 7 is positioned below the lower end 82 of each hoisting machine base 8. Therefore, there is a space between the lower end 82 of each hoisting machine base 8 and the lower end 72 of each deflector mounting beam 7. In this space, the central shaft 61 of the deflector wheel 6 is guided by the two vertical adjustment grooves 9 arranged opposite to each other and moves in the vertical direction. The vertical adjustment groove 9 is formed in the deflector mounting beam 7 at a portion corresponding to this space. The vertical adjustment groove 9 is a through hole. Both ends of the central shaft 61 of the baffle wheel 6 are inserted into these vertical adjustment grooves 9. Both ends of the central shaft 61 of the deflector wheel 6 protrude outside through the vertical adjustment groove 9.

As shown in FIGS. 2B and 3B, springs 10 are provided between the lower surfaces of both ends of the central shaft 61 of the deflector wheel 6 and the upper surfaces of the lower ends 72 of the deflector wheel mounting beams 7. The spring 10 is provided in the vertical direction, that is, in the up-and-down direction. The spring 10 expands and contracts in the vertical direction. The spring 10 constitutes a position control unit that controls the position of the baffle wheel 6 in the vertical direction according to the value of the load in the cage. 2A and 2B show a state where the spring 10 is extended. 3A and 3B show a state where the spring 10 is contracted. The spring 10 supports the baffle wheel 6. The spring 10 can move the deflecting wheel 6 in the vertical direction by expansion and contraction thereof. If the value of the spring constant of the spring 10 is too small, the deflecting wheel 6 cannot be supported. On the other hand, if the value of the spring constant of the spring 10 is too large, a desired amount of displacement cannot be obtained in the spring 10. Therefore, the spring constant of the spring 10 is appropriately selected as appropriate so that the spring 10 can support the deflector wheel 6 and the vertical position of the deflector wheel 6 can be adjusted satisfactorily.
Here, the spring constant is a force required to give a displacement per unit to the spring. That is, the spring constant is a ratio between the load on the spring and the displacement of the spring, and the relationship between them is expressed by the following equation.
Load = spring displacement x spring constant

As shown in FIGS. 2A and 2B, the deflecting wheel 6 when the load in the basket is small is called “the deflecting wheel 6a”, and the spring 10 in that case is called the “spring 10a”. Similarly, as shown in FIGS. 3A and 3B, the deflecting wheel 6 when the load in the basket is large is referred to as a “deflecting wheel 6 b”, and the spring 10 in that case is referred to as a “spring 10 b”. As is apparent from the figure, the compression amount of the spring 10a is smaller than the compression amount of the spring 10b. When the load in the basket becomes small, the deflector 6 moves to the position of the deflector 6a. Thereby, the winding angle θ around the sheave 5 of the rope 3 is reduced. Therefore, the traction generated between the sheave 5 and the rope 3 is reduced. As a result, the deceleration of the car 1 at the time of emergency stop of the brake becomes small. Hereinafter, the winding angle θ when the load in the cage is small is referred to as θa, and the winding angle θ when the load in the cage is large is referred to as θb. Here, the winding angle θ is an angle corresponding to a portion where the rope 3 and the sheave 5 are in contact with each other.

Before explaining the operation of the elevator apparatus according to this embodiment, the principle will be described first.

The deceleration of the car during an emergency stop during driving is based on three factors: (1) inertia of the elevator system, (2) brake torque, and (3) traction between the sheave 5 and the rope 3. Dependent. These three elements are described below.

(1) Inertia of the elevator system The inertia of the elevator system is the inertial force of the elevator system. Normally, when an emergency stop is performed during the operation of the car, when the inertia of the elevator system is small, that is, when the load in the car is small, the deceleration of the car 1 is large, and conversely, when the inertia is large, that is, within the car When the load is large, the deceleration of the basket 1 is small.

(2) Brake torque The brake torque is the torque when the brake of the hoisting machine 4 is stopped. When the brake torque is large, the deceleration of the car 1 increases. Conversely, when the brake torque is small, the deceleration of the car 1 decreases.

(3) Traction between the sheave 5 and the rope 3 The traction between the sheave 5 and the rope 3 of the hoist 4 is a frictional force generated between the rope 3 and the sheave 5. is there. Hereinafter, this frictional force is referred to as traction of the rope 3. By the traction of the rope 3, the rotational force of the hoisting machine 4 is converted into the vertical movement of the cage 1 via the rope 3. Accordingly, the longer the length of the rope 3 wound around the sheave 5, that is, the larger the winding angle θ, the greater the traction of the rope 3. Conversely, the shorter the length of the rope 3 wound around the sheave 5, that is, the smaller the winding angle θ, the smaller the traction. Here, “the length of the rope 3 wound around the sheave 5” means the length of the rope 3 in a portion where the sheave 5 and the rope 3 are in contact, that is, the rope 3 corresponding to the winding angle θ. Length.

Next, the relationship between traction and brake torque will be described.
When the brake torque is smaller than the traction of the rope 3, the deceleration of the car 1 is determined by the brake torque.
On the other hand, when the brake torque is greater than or equal to the traction of the rope 3, before the entire brake torque is generated, slip occurs between the rope 3 and the sheave 5 due to the traction limit. Therefore, the brake torque higher than the traction limit is not transmitted to the basket 1. The traction limit is the maximum value of traction.
From the above, it can be seen that even when the brake torque is constant, the deceleration of the car 1 can be changed by changing the magnitude of the traction.

Next, the relationship between the car deceleration and the car load in a general elevator apparatus will be described. FIG. 7 is a graph showing the relationship between the car deceleration and the car load. In FIG. 7, the vertical axis represents the deceleration of the car 1, and the horizontal axis represents the load factor in the car. The in-car load factor [%] is the car 1 occupancy rate [%].

In a general elevator apparatus, the weight of the weight is set so that the weight of the weight is equal to the sum of the car mass and a half of the car load. That is, the weight of the weight is set so that the weight of the cage and the weight of the weight are balanced when the boarding ratio is 50%. FIG. 7 shows the deceleration of the car when the car is brought to an emergency stop in such an elevator apparatus. In FIG. 7, D ₁ is a graph when the car traveling in the upward direction is in an emergency stop, and D ₂ is a graph when the car traveling in the downward direction is in an emergency stop. The following features can be read from FIG.
(A) The condition for the maximum deceleration of the car is when the load in the car is small and the car is moving downward.
(B) The conditions for the smallest deceleration of the car are when the load in the car is large and the car is moving downward.
(C) When the cage is moving in the downward direction, the deceleration of the cage decreases as the load in the cage increases.
(D) When the cage is moving in the upward direction, the deceleration of the cage increases as the load in the cage increases. That is, the phenomenon is the reverse of the above (c).
(E) The difference between the maximum and minimum values of the car deceleration due to changes in the load factor in the car is when the car is moving upward when the car is moving downward. Bigger than. Note that the difference is the fluctuation range of the deceleration.

Thus, in a general elevator apparatus, the deceleration changes depending on the load factor in the car and the traveling direction. Therefore, a large deceleration may occur when the basket stops emergency. Therefore, in the present embodiment, the occurrence of a large deceleration is suppressed by adjusting the deceleration according to the load variation in the car. Specifically, the vertical position of the deflector wheel 6 is adjusted using the spring 10. Thereby, the traction of the rope 3 is changed and the impact at the time of emergency stop is relieved. In order to alleviate the impact, the deceleration in the case (a) is particularly large. Therefore, it is important to reduce the deceleration in the case (a). Therefore, in the present embodiment, attention is particularly paid to the reduction in deceleration in the case of (a).

The operation of the elevator apparatus according to the present embodiment will be described.
As described above, in the present embodiment, the vertical position of the deflector wheel 6 is adjusted according to the variation in the load in the car 1.
In the present embodiment, a spring 10 and a deflecting wheel mounting beam 7 are provided to adjust the vertical position of the deflecting wheel 6. The baffle mounting beam 7 is provided with a vertical adjustment groove 9. The deflecting wheel 6 is supported by a deflecting wheel mounting beam 7. The central shaft 61 of the deflector wheel 6 is guided by the vertical adjustment groove 9 and moves in the vertical direction. Thereby, the deflector 6 moves in the vertical direction. Specifically, when the load in the cage is small, as shown in FIGS. 2A and 2B, the spring 10 extends and the deflector 6 moves upward. On the other hand, when the load in the cage is large, as shown in FIGS. 3A and 3B, the spring 10 is contracted and the deflecting wheel 6 moves downward.

Thus, when the load in the basket 1 is small, the length of the rope 3 wound around the sheave 5 is short and the winding angle θ is small because the deflecting wheel 6 moves upward. That is, it is in the state of θ = θa shown in FIG. 2A. Thereby, since the contact area of the sheave 5 and the rope 3 becomes small, the traction of the rope 3 falls. For this reason, even if the brake torque of the brake of the hoisting machine 4 is constant, the deceleration of the basket 1 can be reduced.

On the other hand, when the load in the basket 1 is large, the length of the rope 3 wound around the sheave 5 is long and the winding angle θ becomes large because the deflecting wheel 6 moves downward. That is, it is a state of θ = θb shown in FIG. 3A. Thereby, since the contact area of the sheave 5 and the rope 3 becomes large, the traction of the rope 3 rises. For this reason, even if the brake torque of the brake of the hoisting machine 4 is constant, the deceleration of the basket 1 can be increased.

By doing so, the deceleration in the case of the above (a) can be reduced. In addition, regarding the difference (e), the difference when the car 1 is moving downward can be reduced. Thus, this embodiment is particularly effective when the basket is moving downward. When the basket is moving upward, the operation is reversed. Therefore, when the load in the cage is large, the deceleration can be reduced, and this embodiment is effective. On the other hand, when the load in the car is small, the deceleration increases, but there is not much problem because the absolute value of the deceleration is originally small.
Therefore, in the present embodiment, even when the car 1 is in an emergency stop, a large deceleration does not always occur, so that the impact at the time of an emergency stop can be reduced.

As described above, in the present embodiment, the spring 10 is provided so that the vertical position of the baffle wheel 6 is automatically adjusted according to the load variation in the car 1. An automatic adjustment method using the spring 10 will be described below.

As shown in FIG. 8, a load L is applied to the central shaft 61 of the deflecting wheel 6 in an obliquely downward direction from the rope 3 through the deflecting wheel 6. The direction of the load L coincides with the direction of a straight line connecting the contact point P between the rope 3 and the deflector wheel 6 and the center of the deflector wheel 6. At this time, the greater the tension generated in the rope 3, the greater the load L is generated on the central shaft 61 of the deflector wheel 6. The tension generated in the rope 3 increases when the load in the cage 1 is large, and decreases when the load in the cage 1 is small.
As shown in FIG. 8, the load L can be divided into component forces L ₁ and L ₂ . The component force L ₁ is a component force in the downward direction. The component force L ₂ is a component force in a direction parallel to the direction of the rope 3 between the sheave 5 and the deflector wheel 6. Therefore, as the load L increases, the component force L ₁ also increases. Therefore, as the load in the basket 1 increases, the component force L ₁ increases.

Due to this principle, when the load in the basket 1 is small, the component force L ₁ is small, so that the spring 10 extends as shown in FIGS. 2A and 2B. Therefore, the vertical position of the deflector 6 is high.
On the other hand, when the load in the basket 1 is large, the component force L ₁ is large, so that the spring 10 is contracted as shown in FIGS. 3A and 3B. Therefore, the vertical position of the deflector 6 is low.

Thus, in the present embodiment, the vertical position of the deflector 6 is automatically adjusted by the spring 10 in accordance with the fluctuation of the load in the basket 1. The amount of compression of the spring 10 is uniquely determined by the load in the cage 1 and the spring constant. Therefore, by appropriately selecting the spring constant of the spring 10, the deflecting wheel 6 can be adjusted to a desired position by following the load in the basket 1. Therefore, the winding angle θ of the rope 3 can always be automatically adjusted to an optimum value without measuring the load in the cage 1. Therefore, in the present embodiment, there is no need to provide a sensor for measuring the load in the basket 1.

As described above, in the present embodiment, the elevator apparatus includes the sheave 5, the hoisting machine 4 that includes the motor that rotates the sheave 5, and the brake that brakes the sheave 5, and the car 1. The rope 3 connected to the weight 2 and wound around the sheave 5, provided between the sheave 5 and the weight 2, and supported by the sled wheel 6 and the sled wheel 6 around which the rope 3 is wound. As a position control unit that controls the vertical position of the sled wheel 6 according to the value of the sled wheel mounting beam 7 and the load in the basket 1 of the car 1 that enables the sled wheel 6 to move in the vertical direction. And a spring 10. The spring 10 moves the deflecting wheel 6 downward in accordance with an increase in the load in the cage, and moves the deflecting wheel upward in response to a decrease in the load in the cage. Since the traction of the rope 3 can be adjusted by moving the baffle wheel 6 in the vertical direction, it is possible to reduce the impact by controlling the deceleration at the time of emergency stop according to the load in the car.

Further, in the present embodiment, the deflector wheel mounting beam 7 is provided with a vertical adjustment groove 9 that allows the center shaft 61 of the deflector wheel 6 to move only in the vertical direction. Thereby, the central axis 61 can only move up and down, and does not move in the lateral direction. Therefore, the movement of the deflector 6 is stabilized.

Further, in the present embodiment, a spring 10 as a position control unit is provided between the deflector wheel 6 and the lower end 72 of the deflector wheel mounting beam 7. The spring 10 expands and contracts following the change in the load in the cage. Therefore, the vertical position of the deflector 6 is automatically moved by the expansion and contraction of the spring 10. Specifically, when the load in the cage is large, the spring 10 is contracted in accordance with the load in the cage, and the position of the deflecting wheel 6 moves downward. On the other hand, when the load in the cage is small, the spring 10 is extended in accordance with the load in the cage, and the position of the deflector 6 is moved upward. For this reason, by appropriately selecting the spring constant of the spring 10, the moving distance of the deflecting wheel 6 can be arbitrarily determined. Therefore, the winding angle θ of the rope 3 can always be automatically set to an optimum value without measuring the load in the cage 1.

Embodiment 2. FIG.
FIG. 4 is a schematic block diagram showing a configuration of an elevator apparatus according to Embodiment 2 of the present invention. The main difference between the present embodiment and the first embodiment is that an actuator 11 is provided instead of the spring 10 in the present embodiment. Hereinafter, this embodiment will be described in detail.

In the present embodiment, the hoisting machine main body 20 of the hoisting machine 4 is provided with a motor 18, a brake 16, and an encoder 12.

The encoder 12 is a detector that detects the rotation direction of the sheave 5 by detecting the rotation direction of the motor 18. The encoder 12 generates a signal corresponding to the direction of rotation of the sheave 5. The direction of rotation of the sheave 5, that is, the direction of movement of the car 1 can be detected by the sign of the signal from the encoder 12.

Since the other configuration of the hoist 4 is the same as that of the first embodiment, the description thereof is omitted here.

Further, the basket 1 is provided with a scale device 13. The scale device 13 detects the weight in the car 1 as a load in the car. The scale device 13 outputs a signal corresponding to the detected load in the car.

The signal from the encoder 12 and the signal from the scale device 13 are transmitted to the elevator control device 14. Based on these signals, the elevator control device 14 controls expansion and contraction of the actuator 11 via an actuator control device 19 described later. Therefore, in the present embodiment, the elevator control device 14 constitutes an expansion / contraction amount calculation unit that calculates the expansion / contraction amount of the actuator 11 according to the moving direction of the car 1 and the load in the car.

Further, the elevator control device 14 operates the motor 18 of the hoisting machine 4 via the power conversion device 15. Further, the elevator control device 14 operates the brake 16 via the brake control device 17.

In the present embodiment, an actuator 11 is provided for the deflecting wheel 6. The actuator 11 is provided in the vertical direction. The actuator 11 supports the deflector wheel 6. The actuator 11 can move the deflecting wheel 6 in the vertical direction. A signal from the elevator control device 14 is transmitted to the actuator 11 via the actuator control device 19. The actuator 11 is operated by the signal. Thus, the deflecting wheel 6 is moved up and down by the actuator 11.

In the present embodiment, the actuator 11, the scale device 13, the encoder 12, the elevator control device 14, and the actuator control device 19 are arranged in the vertical position of the deflector 6 according to the value of the load in the car. The position control part which controls is comprised.

Next, the configuration of the actuator 11 will be described with reference to FIGS. 5A, 5B, 6A, and 6B. 5A, FIG. 5B, and FIG. 6A, FIG. 6B are partial detailed views of the elevator apparatus according to the present embodiment. 5A and 5B show a case where the load in the car is small, and FIGS. 6A and 6B show a case where the load in the car is large. 5A is a front view, and FIG. 5B is a side view corresponding to FIG. 5A. 6A is a front view, and FIG. 6B is a side view corresponding to FIG. 6A.

The actuator 11 includes an upper end 111, a lower end 112, and an arm 113 that connects the upper end 111 and the lower end 112. The arm 113 of the actuator 11 is provided in the vertical direction, that is, in the up and down direction. The arm 113 of the actuator 11 extends and contracts in the vertical direction. In the present embodiment, as the arm 113 extends and contracts, the deflecting wheel 6 is guided by the vertical adjustment groove 9 and moves up and down.

As shown in FIGS. 5A and 5B, the deflecting wheel 6 when the load in the cage is small is called “the deflecting wheel 6a”, and the actuator 11 in that case is called the “actuator 11a”. Similarly, as shown in FIGS. 6A and 6B, the deflection wheel 6 when the load in the cage is large is referred to as “a deflection wheel 6b”, and the actuator 11 in that case is referred to as an “actuator 11b”.

Thus, in the present embodiment, the actuator 11 supports the deflector wheel 6 and adjusts the vertical position of the deflector wheel 6. Based on the signals from the encoder 12 and the scale device 13, the elevator control device 14 determines whether the actuator 11 is extended or contracted. Moreover, the elevator control apparatus 14 calculates the amount of expansion | extension, when extending, and calculates the amount of contraction, when shortening. The elevator control device controls the actuator control device 19 based on the calculation results. With this control, the actuator control device 19 adjusts the expansion and contraction of the arm 113 of the actuator 11. As the arm 113 expands and contracts, the deflector 6 moves as follows.

(1) When the basket is moving downward:
・ If the load in the basket is small, move the deflector 6 upward.
・ If the load in the basket is large, move the deflector 6 downward.

(2) When the basket is moving upward:
・ If the load in the basket is small, move the deflector 6 downward.
・ If the load in the basket is large, move the deflector 6 upward.

The operation (1) is the same as that in the first embodiment, but the operation (2) is the reverse of the operation in the first embodiment. As can be seen from the graph of FIG. 7, when the car is moving downward, it is desirable to reduce the deceleration when the load in the car is small and increase the deceleration when the load in the car is large. . Therefore, in the present embodiment, the deflector 6 is moved as in (1) above. On the other hand, when the cage is moving upward, it is desirable to increase the deceleration when the load in the cage is small, and decrease the deceleration when the load in the cage is large. Therefore, in the present embodiment, the deflector 6 is moved as in (2) above.
With the above operation, the effect when the car 1 is moving downward is the same as that of the first embodiment. However, when the car 1 is moving upward, compared to the first embodiment, Furthermore, the deceleration of the basket 1 can be reduced.

As described above, in the present embodiment, when the car 11 is moving downward, the actuator 11 moves the deflecting wheel 6 downward in accordance with the increase in the car load, thereby reducing the car load. Accordingly, the deflector 6 is moved upward. On the other hand, when the car 1 is moving in the upward direction, the deflecting wheel 6 is moved upward in accordance with an increase in the car load, and the deflecting wheel 6 is moved downward in accordance with a decrease in the car load.

The amount of expansion / contraction of the actuator 11 is determined as follows, for example.
Two lookup tables are prepared for the case where the car 1 moves upward and the case where it moves downward. In each look-up table, the correspondence between the in-car load factor [%] and the length [cm] of the actuator 11 is determined in advance. For example, in the upward lookup table, when the load factor in the car is 0% or more and less than 20%, the length of the actuator 11 is ◯ cm, and the load factor in the car is 20% or more and less than 40%, The length of the actuator 11 is determined in advance as ΔΔcm,. The same applies to the downward lookup table. Thereby, the elevator control device 14 searches the length of the actuator 11 corresponding to the current in-car load from the lookup table. Then, the elevator control device 14 compares the current length of the actuator 11 with the retrieved length of the actuator 11 to determine the amount of expansion / contraction of the actuator 11.
The method for determining the amount of expansion / contraction of the actuator 11 is not limited to this case. For example, a function using the load in the car as a parameter may be prepared for each case where the car 1 is moved upward and when the car 1 is moved downward. Or you may make it calculate by another method.

Since other configurations and operations are the same as those in the first embodiment, the description thereof is omitted here.

Thus, in the present embodiment, as in the first embodiment, the elevator apparatus includes the rope 3 that connects the cage 1 and the weight 2, the sheave 5 and the baffle 6 on which the rope 3 is wound. And a deflector wheel mounting beam 7 for supporting the deflector wheel 6 so that the vertical position of the deflector wheel 6 can be adjusted. In the present embodiment, as shown in the above (1) and (2), the deflecting wheel 6 is moved upward or downward according to the load in the cage and the moving direction of the cage 1.

As a result, when the car 1 is moving downward and the load in the car is small, and when the car 1 is moving in the upward direction and the car load is large, the deflector 6 Move up. Thereby, the length of the rope 3 wound around the sheave 5 is shortened, and the winding angle θ is decreased. As a result, the traction of the rope 3 is reduced. For this reason, even when the brake torque of the brake of the hoisting machine 4 is constant, the deceleration of the car 1 can be reduced.

On the other hand, when the cage 1 is moving upward and the load in the cage is small, and when the cage 1 is moving downward and the load in the cage is large, the baffle 6 is moved. Move down. Thereby, the length of the rope 3 wound around the sheave 5 is increased, and the winding angle θ is increased. As a result, the traction of the rope 3 increases. For this reason, even when the brake torque of the brake of the hoisting machine 4 is constant, the deceleration of the car 1 can be increased.

As described above, also in the present embodiment, since the vertical position of the deflector 6 is moved in accordance with the load in the car, according to the load in the car as in the first embodiment. Impact can be mitigated by controlling deceleration during emergency stop.

Furthermore, in the present embodiment, the encoder 12 can detect whether the car 1 is moving upward or whether the car 1 is moving downward. Thereby, not only the load in the car but also the moving direction of the car is taken into consideration, and the vertical position of the deflector 6 is moved. As a result, even when the car 1 is moving in either the upward direction or the downward direction, it is possible to always suppress the occurrence of a large deceleration that gives an impact to the passengers. It is possible to reduce the fluctuation range.

In the present embodiment, the position control unit detects the rotation direction of the motor 18 by detecting the rotation direction of the retractable actuator 11 that supports the deflector, the scale device 13 that measures the load in the basket, and the motor 18. An encoder 12 that detects the movement direction of 1, and an expansion / contraction amount calculation unit that calculates the expansion / contraction amount of the actuator 11 based on the load in the cage measured by the scale device 13 and the movement direction of the cage 1 detected by the encoder 12. As an elevator control device 14 and an actuator control device 19 for expanding and contracting the actuator 11 based on the expansion and contraction amount calculated by the expansion and contraction amount calculation unit. The actuator 11 controls the vertical position of the deflector 6 by expanding and contracting according to the variation in the load in the cage and the moving direction of the cage. Thereby, the actuator 11 can control the position of the deflector 6 according to the fluctuation | variation of the load in a cage | basket | car and the moving direction of a cage | basket | car. The above-described first embodiment is effective particularly when the cage 1 is moving in the downward direction, but in this embodiment, it is effective in both the upward and downward directions.

In the present embodiment, when the car 1 is moving downward, the actuator 11 moves the deflecting wheel 6 downward in accordance with an increase in the load in the car, and the deflecting wheel in response to a decrease in the load in the car. 6 is moved upward. On the other hand, when the car 1 is moving in the upward direction, the deflecting wheel 6 is moved upward in accordance with an increase in the car load, and the deflecting wheel 6 is moved downward in accordance with a decrease in the car load. Thereby, even when the cage 1 is moving in either the upward direction or the downward direction, it is possible to prevent unnecessary large deceleration from occurring. Further, even when the car 1 is moving in either the upward direction or the downward direction, the fluctuation range of the deceleration can be reduced.

Claims

A hoisting machine comprising a sheave, a motor that rotates the sheave, and a brake that brakes the sheave;
A rope connected to the cage and the weight, wound around the sheave,
A sled wheel provided between the sheave and the weight and wound with the rope;
A baffle mounting beam that supports the baffle and allows vertical movement of the baffle;
A position control unit that controls a position of the baffle in a vertical direction according to a value of a load in the basket of the basket;
The position control unit moves the deflector downward according to the increase in the basket load, and moves the deflector upward according to the decrease in the basket load.
Elevator device.
The elevator apparatus according to claim 1, wherein the deflecting wheel mounting beam is provided in a vertical direction, and has a vertical adjustment groove into which a shaft of the deflecting wheel is inserted and guides the vertical movement of the shaft.
The position control unit is composed of a spring that supports the deflector,
The elevator apparatus according to claim 1, wherein the spring controls a position in a vertical direction of the deflecting wheel by expanding and contracting according to a change in the load in the car.
The position controller is
An extendable actuator that supports the deflector;
A weighing device for measuring the load in the basket;
An encoder that detects a moving direction of the basket by detecting a rotation direction of the motor;
An expansion / contraction amount calculation unit that calculates the expansion / contraction amount of the actuator based on the load in the cage measured by the scale device and the moving direction of the cage detected by the encoder;
Based on the expansion / contraction amount calculated by the expansion / contraction amount calculation unit, the actuator control device is configured to extend / contract the actuator,
The elevator apparatus according to claim 1 or 2, wherein the actuator controls a position in a vertical direction of the deflector by extending and contracting in accordance with a change in the load in the car and a moving direction of the car.
The actuator is
When the basket is moving downward, the baffle is moved downward according to the increase in the basket load, the baffle is moved upward according to the decrease of the basket load,
When the car is moving in the upward direction, the baffle is moved upward in accordance with an increase in the load in the car, and the baffle is moved downward in accordance with a decrease in the car load.
The elevator apparatus according to claim 4.