JP2003212450A - Traction type elevator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a traction type elevator capable of rapidly stopping a car while sufficiently and certainly securing a frictional force between a hoist sheave and a main rope in an emergency braking time by a hoist brake, without changing a hanging method of the main rope on the hoist sheave and a groove shape of the hoist sheave and without decreasing service life of the main rope. <P>SOLUTION: In the traction type elevator, the hoist sheave 1 is braked by the hoist brake 7 in an emergency. The car 3 driven by the hoist sheave 1 is provided with an auxiliary braking device 12 having a brake shoe connectable to guide rails 5a and 5b by pressure. In the emergency braking time by the hoist brake 7, the auxiliary braking device 12 is operated to connect the brake shoe to the guide rails 5a and 5b by pressure and brakes them. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a traction type elevator driven by a hoisting machine.

[0002]

2. Description of the Related Art In a traction type elevator, a main rope hung on a hoisting machine sheave hangs a car and a counterweight below the hoisting machine sheave, and a car and a counterweight are rotated in the hoistway of a building. It is designed to go up and down.

In an emergency such as an operation of a safety circuit during operation of an elevator or a power failure, emergency braking is performed to control the car to make an emergency stop. This emergency braking is a mechanism to stop the car by braking the hoisting machine sheave with the hoisting machine brake and braking the main rope hung on the hoisting machine sheave with friction with the hoisting machine sheave. There is.

Considering the frictional force between the hoisting machine sheave and the main rope in a high-stroke, large-capacity or ultra-high speed elevator, the frictional force is sufficient in normal operation, but during emergency braking by the hoisting machine brake. There is a case that the sheave of the hoisting machine and the main rope slip due to lack of space.

This is because in normal operation, the rotational acceleration / deceleration of the hoisting machine sheave is kept constant by control of the operation, while in emergency braking, the hoisting machine brake is forcibly braked, so that the loading of the car This is because the deceleration increases depending on the conditions.

Since the hoisting machine brake is set to have a constant deceleration when the amount of unbalance between the car and the counterweight is the largest, when the car and the counterweight are in balance, The deceleration will be more than that.

For this reason, the acceleration / deceleration of the car is greater during emergency braking than during normal operation, and the weight of the suspended heavy object of the hoisting machine is heavier in a high stroke, large capacity, or ultra-high speed elevator. In addition, since the traveling speed of the car is high, the inertial force of the car and the counterweight in the traveling direction becomes large, so that rope slip occurs.

Further, in a large capacity elevator, the unbalance amount of the car and the counterweight becomes large when the load of the car is around 0% or 100%, and the inertial force in the traveling direction of the car and the counterweight becomes large. Become.

Conventionally, as a means for sufficiently securing the frictional force between the hoisting machine sheave and the main rope, the method of hanging the main rope on the hoisting machine sheave is changed from single wrap to double wrap, The groove shape of the hoisting sheave on which the rope hangs is designed to increase the frictional force, for example, by changing the groove shape so that the undercut angle is widened.

As another means for preventing the occurrence of rope slip between the hoisting machine sheave and the main rope at the time of emergency stop, a braking force urging means is provided in the hoisting machine brake to prevent rope slipping. A method of controlling a braking force, a method of gripping a main rope by a hoisting machine sheave and a braking member, and the like have been proposed.

[0011]

However, in a high stroke or large capacity elevator, in order to increase the frictional force between the sheave of the hoisting machine and the main rope, the method of changing the main rope from the single lap to the double lap is adopted. When,
The number of grooves in the hoisting machine sheave doubles, the axial dimension of the hoisting machine sheave expands accordingly, and it becomes necessary to increase the strength of the hoisting machine itself. The impact will occur. Moreover, since the shape of the hoisting machine itself becomes large, the machine room for accommodating the hoisting machine must be expanded.

In the double wrap, since the winding angle of the main rope is increased, the bending fatigue of the rope is increased, the rope life is shortened, the rope replacement period is shortened, and the running cost of the elevator is increased.

Further, if a means for widening the undercut angle of the hoisting machine sheave is adopted, the frictional force is increased, but the rope is severely worn, the rope life is shortened, and the running cost of the elevator is also increased.

The increase in the frictional force between the hoisting machine sheave and the main rope at the time of emergency braking is effective only when the safety circuit is activated or during an emergency such as a power failure. Is unnecessary, even during normal operation where it is not necessary to increase, and as a result, the rope life is unnecessarily reduced.

Further, in the method of providing the braking force energizing means to the hoisting machine brake, the control means does not work when the power is cut off due to a power failure or the like, and the speed is high in the case of an ultra high speed elevator. Even if control is performed to increase the braking force of the brake, it becomes difficult to secure a sufficient frictional force between the hoisting machine sheave and the main rope.

Further, in the method of gripping the main rope with the hoisting machine sheave and the braking member, the main rope slides on the braking member, so that the rope is severely worn and the life is shortened.

The present invention has been made by paying attention to such a point, and an object thereof is to change the way of hanging the main rope on the hoisting machine sheave and the groove shape of the hoisting machine sheave, and A traction elevator that can stop the car in an emergency by ensuring the friction force between the hoisting machine sheave and the main rope during emergency braking by the hoisting machine brake without shortening the life of the main rope. To provide.

[0018]

According to a first aspect of the present invention, a car and a counterweight are hung by a main rope hung on a hoisting machine sheave, and the hoisting machine sheave is braked by an hoisting machine brake in an emergency. In a traction elevator where braking is applied to the car or counterweight, an auxiliary braking device equipped with a guide rail that guides the travel of the car or counterweight and a brake shoe that can be pressed into contact is provided, and emergency braking by hoisting machine brakes is performed. This auxiliary brake device is sometimes operated to bring the brake shoe into pressure contact with the guide rail to apply braking.

The invention according to claim 2 is characterized in that the auxiliary brake device operates based on a signal from the elevator control panel during emergency braking by the hoisting machine brake.

The invention according to claim 3 is characterized in that it comprises means for informing the elevator control panel of the operating state of the auxiliary brake device.

According to a fourth aspect of the present invention, in the auxiliary brake device, the elastic force of the spring brings the brake shoe into pressure contact with the guide rail to apply braking, and hydraulic pressure resists the elastic force of the spring to cause the brake shoe to guide the brake shoe. It is characterized in that the brake release state is maintained by separating from.

The invention according to claim 5 is characterized in that it is provided with a hydraulic pressure generation unit for holding the hydraulic pressure for releasing the brake.

The invention according to claim 6 is characterized in that it has a mechanism for returning oil to the oil tank in the hydraulic pressure generating unit when the air in the hydraulic pipe of the auxiliary brake device is deflated.

According to a seventh aspect of the present invention, a car or a counterweight provided with an auxiliary brake device is provided with a roller guide for rolling up and down the car or the counterweight by rolling contact with the guide rail of the car or the counterweight, and the auxiliary brake when the brake is released. The clearance between the brake shoe of the device and the guide rail is larger than the horizontal movement allowance of the roller guide with respect to the guide rail.

The invention described in claim 8 is characterized in that brake release means capable of releasing the brake of the auxiliary brake device via the auxiliary power source is provided after the emergency braking by the hoisting machine brake. There is.

According to a ninth aspect of the present invention, at the time of power failure, the timer automatically brakes the power of the auxiliary power source after the elapse of a preset time from the power failure until the car stops due to emergency braking. It is characterized by being opened.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 schematically shows the entire structure of an elevator installed in a hoistway of a building. A main rope 2 is wound around a hoisting sheave 1, and a car 3 and a balance are balanced by the main rope 2. A weight 4 is suspended below the hoisting machine sheave 1, and the car 3 and the counterweight 4 are lifted in opposite directions along the guide rails 5 and 6 in the hoistway by the rotation of the hoisting machine sheave 1.

A hoisting machine brake 7 is attached to the hoisting machine sheave 1, and emergency braking for the hoisting machine sheave 1 is performed by the hoisting machine brake 7.

Below the car 3 and the counterweight 4, the weight of the main rope 2 from the top of the car 3 to the hoisting sheave 1 and the weight of the main rope 2 from the top of the counterweight 4 to the hoisting sheave 3 are shown. A compensating rope 10 for canceling the imbalance with the weight is hung, and a compensating sheave 11 is provided at the lowermost portion of the compensating rope 10 for appropriately maintaining the tension of the compensating rope 10 and stabilizing the operation.

On the upper part of the car 3, an auxiliary braking device 12 is installed which operates in conjunction with the hoisting machine brake 7 during emergency braking by the hoisting machine brake 7.

FIG. 2 shows a schematic structure of the auxiliary brake device 12. This auxiliary brake device 12 is provided with a pair of hydraulic clampers 13a and 13b, and these hydraulic clampers 13a and 13b are provided above the car 3. It is arranged on both sides.

The car 3 has a car frame 15, and the car frame 1
5, brackets 16a and 16b are provided on both sides of the upper portion of the roller 5, and the roller guide 1 is attached to the brackets 16a and 16b.
7a, 17b are rotatably provided, and the roller guides 17a, 17b are provided on both sides of the car 3 with guide rails 5a,
It is adapted to guide the traveling of the car 3 by rolling on the car 5b.

The pair of hydraulic clampers 13a, 13b of the auxiliary brake device 12 are attached to the brackets 16a, 16b so as to face the guide rails 5a, 5b.

A hydraulic pressure generating unit 20 is installed on the upper beam 15a of the car frame 15, and the hydraulic pressure generating unit 20 and each of the hydraulic clampers 13a and 13b are connected by a hydraulic hose 21. The hydraulic pressure generating unit 20 includes an elevator control panel 22 installed in a machine room or the like above the hoistway.
Is connected to a power line 24 and a signal line 25 which are led out through an auxiliary power source 23 such as an emergency battery.

3 and 4, the hydraulic clamper 13 is shown.
The structure of a and 13b is shown. Hydraulic clamper 13a,
13b includes a pair of hydraulic cases 27 facing each other with the guide rails 5a and 5b interposed therebetween.
Brake shoes 28 are provided at the end portions of the brake levers 7 so as to face the guide rails 5a and 5b, respectively.

A hydraulic hose 21 derived from the hydraulic pressure generating unit 20 is connected to each hydraulic case 27. A spring 29 for elastically pressing the brake shoe 28 toward the guide rails 5a and 5b is provided in each hydraulic case 27.
Is housed.

During normal operation, the spring 29 is pushed back against the elastic force by the hydraulic pressure sent from the hydraulic pressure generating unit 20 into the hydraulic case 27, and the brake shoe 28 is separated from the guide rails 5a, 5b. Holds open.

FIG. 3 shows the state when the brake is released. The gap h between the brake shoes 28 and the guide rails 5a, 5b is set in the roller guides 17a, 17b so that the brake shoes 28 do not come into contact with the guide rails 5a, 5b even if the car 3 shakes during normal operation. The size is set to be larger than the horizontal movement allowance with respect to the guide rails 5a and 5b.

The brake shoe 28 and the guide rail 5a,
It is also possible to make the gap h between the brake shoe 28 and the guide rails 5a and 5b constant by reducing the gap h between the brake shoe 28 and the guide rails 5b, but in this case, the structure becomes complicated and In this embodiment, the hydraulic clampers 13a and 13b are of the cage fixed type, because dust and the like accumulate in the gaps and require maintenance.

FIG. 5 shows a hydraulic piping system diagram of the hydraulic pressure generating unit 20. The hydraulic pressure generating unit 20 has a unit case 30, and a hydraulic pump 32 driven by a motor 31 is provided in the unit case 30. ing.

The hydraulic pump 32 is connected to the hydraulic clampers 13a and 13b of the auxiliary brake device 12 through the hydraulic hose 21 by the pipe 33, and the check valve 34 is provided in the middle of the pipe 33.

From the middle of the pipe 33, the first and second branch pipes 36 and 37 leading to the oil tank 35 are led out, and the first
A pressure valve 38 is provided in the middle of the branch pipe 36 of the second branch pipe 37.
Solenoid valves 39 are provided in the middle of each. Further, a detection pipe 40 is branched from the middle of the pipe 33, and a differential pressure type pressure switch 41 for brake release confirmation and a differential pressure type pressure switch 42 for motor control are connected to the detection pipe 40, respectively.

Further, the air vent pipe 43 is led out from the hydraulic clampers 13a and 13b of the auxiliary brake device 12,
The air vent pipe 43 communicates with the oil tank 35, and a stop valve 44 is provided in the air vent pipe 43.

During normal operation of the elevator, the electromagnetic valve 39 in the hydraulic pressure generating unit 20 is closed by the brake release signal transmitted from the elevator control panel 22 via the signal line 25, and the electric power supplied via the power line 24 is supplied. As a result, the motor 31 rotates and the hydraulic pump 32 operates.

At this time, the stop valve 44 is closed, the hydraulic pressure due to the operation of the hydraulic pump 32 is transmitted from the pipe 33 to the hydraulic clampers 13a and 13b through the hydraulic hose 21, and the hydraulic pressure causes the spring 29 to resist the elastic force. Then, the brake shoe 28 is pushed back and operates so as to be separated from the guide rails 5a and 5b, and the brake is released.

When the hydraulic pressure in the hydraulic clampers 13a and 13b reaches the brake release pressure, the brake release confirmation pressure switch 41 is activated, and a brake release achievement signal is sent to the elevator control panel 22.

Even after the brake shoe 28 is opened, the hydraulic pressure in the hydraulic clampers 13a, 13b rises, and when the hydraulic pressure reaches a predetermined hydraulic pressure, the motor control differential pressure type pressure switch 42 is actuated. The energization of 31 is cut off, the hydraulic pump 32 is stopped, and the check valve 34 maintains the hydraulic pressure. The hydraulic pressure after the motor 31 is stopped is effectively maintained by the pressure accumulation effect of the hydraulic hose 21.

When the pressure drop of the hydraulic pressure occurs, the differential pressure type pressure switch 42 for motor control is actuated and the motor 31 is restarted, whereby the hydraulic pressure rises and the brake open state of the brake shoe 28 is maintained as it is. .

By repeating such operation, the brake release state of the auxiliary brake device 12 is always maintained while the brake release signal is sent from the elevator control panel 22. Under this condition, normal operation of the elevator is performed by controlling the hoisting machine sheave 1.

The differential pressure type pressure switch 4 for motor control is used.
The pressure drop detection level of 2 is set to a value larger than the pressure at which the brake shoe 28 finishes the opening operation.
Therefore, even when the motor 31 is restarted, the brake shoe 28 maintains the open state. When the motor control differential pressure type pressure switch 42 does not operate due to a failure or the like, the hydraulic hose 21 and the hydraulic clampers 13a, 13 are used.
The pressure valve 38, which is set to a value equal to or lower than the oil pressure resistance of b, operates, and the oil is returned to the oil tank 35. Therefore, when the motor 31 operates for a certain period of time, it can be determined that there is a failure such as oil leakage.

In an emergency of the elevator, the hoisting machine brake 7 is activated and the hoisting machine sheave 1 is subjected to emergency braking.
The cases in which the emergency braking by the hoisting machine brake 7 occurs can be roughly classified into when the safety circuit of the elevator control system is activated and when the power failure occurs.

Hoisting machine brake 7 based on the operation of the safety circuit
At the time of emergency braking by the brake control signal from the elevator control panel 22, the electromagnetic valve 39 is opened by the brake control signal and the hydraulic clampers 13a and 13b are opened.
Part of the oil inside is returned to the oil tank 35 by the pressure of the spring 29.

As a result, each hydraulic clamper 13a, 13b
As the hydraulic pressure in the inside decreases, the springs 29 press the respective brake shoes 28 in the direction of approaching the guide rails 5a, 5b and press-contact the side surfaces of the guide rails 5a, 5b. The frictional force between the brake shoe 28 and the guide rails 5a and 5b due to this pressure contact applies braking to the raising / lowering operation of the car 3.

This operation will be described in detail with reference to the time chart shown in FIG. 6. First, the solenoid valve 39 is closed by the signal of the safety circuit, the motor 31 is started and the hydraulic pump 32 is operated, and the hydraulic pressure is increased. It rises to about 10.8Mpa. Due to this increase in oil pressure, the auxiliary brake device 12 is activated and the brake shoe 28 is opened.

When the hydraulic pressure rises to about 12 MPa,
The brake release confirmation differential pressure type pressure switch 41 is turned on, and it is confirmed that the auxiliary brake device 12 is released.

When the hydraulic pressure further rises to about 14.5 MPa, the motor control differential pressure type pressure switch 42 is turned on, the electric current to the motor 31 is cut off, and the operation of the hydraulic pump 32 is stopped.

When the hydraulic pressure drops to about 13 MPa after stopping the hydraulic pump, the differential pressure type pressure switch 41 for brake release confirmation
Is turned off, the motor 31 is started again, the hydraulic pump 32 is activated, and the hydraulic pressure is increased. During this time, the auxiliary brake device 12
Keeps open.

During emergency braking by the hoisting machine brake 7,
The solenoid valve 39 is opened by the brake closing signal from the elevator control panel 22, the hydraulic pressure is lowered, and the auxiliary brake device 12
The brake shoe 28 is pressed against the guide rails 5a and 5b to apply braking.

Further, at the time of power failure, the electric power supplied to the motor 31 and the solenoid valve 39 is cut off, so that the motor 3
1 stops and the solenoid valve 39 opens to reduce the hydraulic pressure in the hydraulic clampers 13a and 13b, and the elastic force of the spring 29 causes the brake shoes 28 to move to the guide rails 5.
It is crimped to a and 5b, and braking is applied.

Thus, in an emergency, the hoisting machine brake 7
The braking by the auxiliary braking device 12 is performed together with the emergency braking by the operation of.

During the emergency braking by the hoisting machine brake 7, the most severe condition that the hoisting machine sheave 1 and the main rope 2 slip is that the car 3 is at maximum load and the car 3
When the car 3 is lowered, and when the car 3 is raised with the car 3 being loaded in the minimum state.

In both of the above two conditions, the amount of imbalance between the car 3 and the counterweight 4 is large, the inertial force in the traveling direction increases, and the sheave 1 of the hoisting machine and the main rope 2 at the acceleration / deceleration during normal operation. Even if the frictional force between them is sufficient, the deceleration becomes too large during emergency braking, and the frictional force between the hoisting machine sheave 1 and the main rope 2 becomes insufficient, causing rope slip.

At the time of emergency braking by the hoisting machine brake 7, when the auxiliary brake device 12 is activated and the brake shoe 28 thereof is pressed against the guide rails 5a and 5b and slides, the traveling direction of the car 3 is determined. A reverse force is generated, therefore the inertial force in the traveling direction of the car 3 is weakened, the frictional force between the hoisting machine sheave 1 and the main rope 2 is sufficiently maintained, and the main rope 2 of the hoisting machine sheave 1 is prevented. Slip can be suppressed.

Generally, the car 3 has a guide rail 5
An emergency stop device that engages with a and 5b by a wedge action is provided. This emergency stop device operates when the speed of the car 3 exceeds a certain level due to some trouble.
To stop the auxiliary brake device 12 of the present invention.
Is different in its function.

After the hoisting machine brake 7 and the auxiliary braking device 12 are actuated by the power failure and the car 3 is stopped by the operation of the hoisting machine brake 7, the passengers in the car 3 are rescued. After the car 3 is once stopped, braking of the car 3 by the auxiliary braking device 12 is no longer necessary. Therefore, during the rescue operation, the auxiliary power source 23 is turned on by the operation of the worker, and the power of the auxiliary power source 23 is supplied to the power line 24. And to the hydraulic pressure generation unit 20 via the signal line 25. Then, the electromagnetic valve 39 is closed by the power of the auxiliary power source 23, the motor 31 is activated to open the brake shoe 28, and the car 3 by the auxiliary brake device 12 is opened.
Release the braking of.

As a result, passengers in the car 3 can be quickly rescued without affecting the elevator system.

By the way, as shown by the chain line in FIG. 2, a timer 45 is incorporated in the auxiliary power supply 23, and this timer 45 is activated when a power failure occurs, and automatically when this timer 45 counts a certain time. The auxiliary power supply 23 is turned on to supply the electric power to the hydraulic pressure generating unit 20,
1 and the solenoid valve 39 are operated to operate the auxiliary brake device 12
It is also possible to release the braking of. In this case, as the fixed time counted by the timer 45,
Emergency braking from the time the power was cut off due to a power failure
Set a time longer than the time it takes to stop.

When the stop valve 44 is normally opened and the motor 31 is operated in this state, oil is transferred from the oil tank 35 to the hydraulic pump 32, the hydraulic hose 21, and the hydraulic clamper 13.
It circulates so as to return to the inside of the oil tank 35 through the a and 13b and the air vent pipe 43. Therefore, the auxiliary brake device 1
When air in the hydraulic clampers 13a, 13b and the hydraulic hose 21 is required to be installed or maintained, the stop valve 44 is repeatedly opened and closed while the motor 31 is being operated to easily and efficiently remove the air. be able to.

As described above, according to this traction type elevator, since the auxiliary brake device 12 is activated during the emergency braking by the hoisting machine brake 7 to reduce the inertial force in the traveling direction of the car 3, the hoisting during the emergency braking is performed. It is possible to improve the lack of frictional force between the machine sheave 1 and the main rope 2.

Since the operation state of the brake opening / closing of the auxiliary brake device 12 is notified to the elevator control panel 22, it is possible that the elevator is mistakenly operated under the operating condition of the auxiliary brake device 12 to cause an operation trouble of the car 3. Inconvenience can be prevented.

Since the auxiliary brake device 12 is operated by a mechanical mechanism using the spring 29, it can be operated accurately even in an emergency due to a power failure. Since the brake is released by the hydraulic mechanism, the pressure required to release the brake can be easily maintained, the power consumption can be reduced compared to the pneumatic type and electromagnetic type, and the brake opening time can be shortened.
The cost can be reduced and the operation time of the elevator is not affected.

The air bleeding work during installation and maintenance of the auxiliary brake device 12 can be easily and efficiently performed by opening and closing the valve 44, and oil will not be scattered into the hoistway due to a work mistake, and Even a worker who does the pulling work for the first time can easily perform the work. This shortens the work time for installation and maintenance of the auxiliary brake device 12, and also leads to a reduction in the total cost of installing the elevator.

Brake shoe 2 of auxiliary braking device 12
8 and the guide rails 5a, 5b are set to have a larger gap than the horizontal movement allowance of the roller guides 17a, 17b. Therefore, when the car 3 travels, the brake shoe 28 and the guide rails 5a, 5b contact each other. Is avoided,
This makes it possible to prevent the ride quality of the car 3 from decreasing.

Furthermore, since the gap between the brake shoe 28 and the guide rails 5a and 5b is large, dust or the like is less likely to collect in the gap, and fine adjustment of the brake gap is unnecessary, which reduces the burden of maintenance work. can do.

Although the auxiliary braking device 12 is installed in the car 3 in the above embodiment, the installation of the auxiliary braking device 12 increases the overall weight of the car 3 and affects the installation of the elevator. In such a case, for example, when it becomes necessary to increase the number of main ropes 2 to be used due to an increase in the weight of the car 3, the auxiliary brake device 1
It is also possible to install 2 on the counterweight 4.

In this case, the auxiliary brake device 12 is installed so that the hydraulic clampers 13a, 13b are opposed to each other with the guide rails 6a, 6b for guiding the traveling of the counterweight 4 separated from each other, and the brakes of the hydraulic clampers 13a, 13b are arranged. The shoe 28 is opposed to the side surfaces of the guide rails 6a and 6b. Then, the brake shoes 28 are operated in the same manner as in the above embodiment.

[0077]

As described above, according to the present invention,
The auxiliary brake device operates during emergency braking by the hoisting machine brake, and the lack of friction between the hoisting machine sheave and the main rope during emergency braking is improved. It is possible to prevent slipping between the hoisting machine sheaves, thus changing the method of hanging the main rope on the hoisting machine sheave from single wrap to double wrapping and changing the groove shape of the hoisting machine sheave. Appropriate braking can be applied to the weight to make an emergency stop.

Since it is not necessary to change the method of hanging the main rope on the hoisting machine sheave from the single wrap to the double wrapping, or to change the groove shape of the hoisting machine sheave,
This makes it possible to reduce the size of the hoisting machine sheave and extend the life of the main rope, prevent the machine room of the elevator from increasing in size, and reduce the running cost for maintenance of the elevator.

[Brief description of drawings]

FIG. 1 is a configuration diagram schematically showing an overall configuration of a traction type elevator according to an embodiment of the present invention.

FIG. 2 is an explanatory diagram showing a configuration of a main part of the traction type elevator.

FIG. 3 is a partially cutaway plan view showing an auxiliary braking device for the traction type elevator.

FIG. 4 is a side view of the auxiliary brake device.

FIG. 5 is a hydraulic circuit diagram showing a hydraulic circuit of a hydraulic pressure generating unit that controls the auxiliary brake device.

FIG. 6 is a time chart for explaining the operation of the auxiliary brake device controlled by the hydraulic pressure generation unit.

[Explanation of symbols]

1 ... Hoisting machine sheave 2 ... Main rope 3 ... basket 4… Balanced weight 5a, 5b ... Car guide rails 6a, 6b ... Guide rails for counterweight 7 ... Hoisting machine brake 12 ... Auxiliary brake device 13a, 13b ... Hydraulic clamper 17 ... Roller guide 20 ... Hydraulic pressure generation unit 22 ... Elevator control panel 23 ... Auxiliary power supply 28 ... Brake shoes 29 ... Spring 31 ... Motor 32 ... Hydraulic pump 34 ... Check valve 35 ... Oil tank 38 ... Pressure valve 39 ... Solenoid valve 41 ... Differential pressure type pressure switch for brake release confirmation 42 ... Differential pressure type pressure switch for motor control 43 ... Air bleeding pipe 44 ... Stop valve 45 ... Timer

Claims (9)

[Claims] 1. A traction type elevator in which a car and a counterweight are hung by a main rope hung on a hoisting machine sheave, and a hoisting machine brake applies braking to the hoisting machine sheave in an emergency. The counterweight is provided with an auxiliary brake device that includes a guide shoe that guides the travel of the car or the counterweight and a brake shoe that can be pressed into contact with the counterweight. Traction type elevator characterized by being pressed against a guide rail to apply braking. 2. The traction type elevator according to claim 1, wherein the auxiliary braking device operates based on a signal from the elevator control panel during emergency braking by the hoisting machine brake. 3. The traction type elevator according to claim 1, further comprising an informing means for informing an elevator control panel of an operating state of the auxiliary brake device. 4. An auxiliary brake device, wherein the brake shoe is pressed against the guide rail by the elastic force of the spring to apply braking, and the brake shoe is separated from the guide rail by hydraulic pressure against the elastic force of the spring to release the brake. The traction elevator according to claim 1, 2 or 3, wherein 5. The traction elevator according to claim 4, further comprising a hydraulic pressure generation unit for holding a hydraulic pressure for releasing the brake. 6. The traction type elevator according to claim 5, further comprising a mechanism for returning oil to an oil tank in a hydraulic pressure generating unit when air is removed from the hydraulic pipe of the auxiliary brake device. 7. A car or a counterweight having an auxiliary brake device is provided with a roller guide for rolling up and down the car or the counterweight by rolling contact with the guide rail, and the brake shoe and the guide of the auxiliary brake device when the brake is released. The traction elevator according to any one of claims 1 to 6, wherein the clearance between the rail and the rail is larger than the horizontal movement allowance of the roller guide with respect to the guide rail. 8. A brake releasing means is provided which is capable of releasing the brake of the auxiliary braking device via the auxiliary power source after the emergency braking by the hoisting machine brake. The traction elevator according to any of the above. 9. In the event of a power failure, the timer automatically causes the auxiliary brake device to release the brakes after a preset time from the power failure until the car stops due to emergency braking. The traction elevator according to claim 8.