JPS6374880A - Hydraulic elevator - Google Patents

Abstract

(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic elevator whose speed is controlled by controlling the flow rate of pressure oil supplied to or discharged from a hydraulic cylinder.

[Prior Art] Conventionally, in this type of hydraulic elevator, the speed of each ride has been controlled by sequentially operating flow control valves hydraulically or mechanically.

In this speed control, running speeds such as acceleration, deceleration, full-speed running speed P and landing running speed change with changes in oil temperature or load. For this reason.

The time spent traveling at the landing speed increases, which often has a negative impact on the psychology of each passenger.

On the other hand, in order to shorten the vehicle's landing time, attempts have also been made to control methods that delay the deceleration command for the corners of the vehicle.

Note that this type of device is disclosed in Japanese Patent Application Laid-Open No. 53-145252.
No. 57-199770.

[Problem that the invention seeks to solve]

However, in this control method, the various flow control valves are set to a constant deceleration delay time, even though the valve characteristics of the flow control valves change due to variations during machining and adjustment. Even if the floor travel time was shortened, it was not possible to always control the floor landing time to a constant level, and floor landing errors occurred, causing problems in terms of ride comfort for passengers.
An object of the present invention is to correct the running characteristics of a hydraulic elevator that change depending on the load or oil temperature using a simple control circuit configuration, and to provide a hydraulic elevator with good riding comfort by always keeping the running time at a landing speed constant. It is about providing.

[Means for solving problems]

The above object is to provide a hydraulic elevator in which a car is raised and lowered by a hydraulic device including a hydraulic cylinder and a flow control valve, and when landing on a floor, the car is decelerated from a predetermined deceleration start point and runs at a low landing speed. means for determining a floor-floor travel time during which the vehicle travels at a floor-landing travel speed; a storage means for storing calculation elements for calculating a deceleration delay time for delaying the start of deceleration from the deceleration start point; a modifying means for determining a difference between a given target value of the flooring travel time and modifying the calculated element according to the determined difference; and a modifying means for calculating the calculated element stored in the storage means by the modifying means. means for updating the deceleration delay time to the corrected deceleration delay time; and an output means for outputting a command to delay the start of deceleration by the deceleration delay time calculated from the calculation element from the deceleration start point, This is achieved by controlling the deceleration of the hydraulic system.

[Effect]

The calculation elements for calculating the deceleration start time for delaying the deceleration command are adaptively modified according to the difference between the floor landing time during which the hydraulic elevator travels at the floor landing speed and its target value. You can drive the car in the time it takes to land on the floor.

〔Example〕

An embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 shows the configuration of a hydraulic elevator according to the present invention, in which a control device section consisting of a control device 5 having an arithmetic function, an electromagnetic control valve 4, a hydraulic drive section consisting of a flow rate control valve 6, a hydraulic cylinder 9, and a control target. The main component is Naru Sakae Kago 12. The control command device 1 excites the electromagnetic control valve 4, and the flow control valve 6 controls the flow rate of pressure oil supplied from the hydraulic pump 3 to the hydraulic cylinder 9 by driving the motor 2, or discharges the pressure oil from the hydraulic cylinder 9 to a tank (not shown). By controlling the flow rate of pressure oil to
Controls the raising or lowering of the plunger 9' of the hydraulic cylinder 9.

7.8 is a detector for detecting oil temperature and load, 13, (1
3') is a switch that operates when deceleration starts when car 12 ascends or descends, 14° (14') is switch 1 for car 1
2 shows a switch that operates when it goes up or down and stops.

Although FIG. 1 shows a system in which the seat 12 is supported via a pulley 10 and a rope 11, there is also a system in which the seat 12 is directly connected to the top of the plunger 9'. One end of the rope 11 is fixed, and the other end is fixed to the seat 12, and when the plunger 9' is raised or lowered, the seat 12 is also raised or lowered.

Here, the electromagnetic control valves 4 are provided with two each for raising and lowering, as shown in FIG. 2, and two solenoids 01. U2 (
Di, D2) are excited at the same time, the flow rate of pressure oil flowing through the flow control valve 6 gradually increases, and the car 12 is started and accelerated to rise (or fall) at full speed. And a switch 13 provided at the deceleration start point. (13') is switched between the rider and 12, the control command device 1 controls the solenoid Ul, (
Di) is de-energized. Therefore, the flow rate of the pressure oil flowing through the flow control valve 6 decreases, and the first power valve 12 starts to decelerate. This point corresponds to point A in FIG. After that, the passenger car 12 finishes decelerating and runs at a constant speed (landing speed). Switch 14 provided in the stop position. (14') and 12, the control command device 1 de-energizes the solenoid U2° (D2). As a result, the flow control valve 6
The flow rate of the pressurized oil flowing through becomes zero, and the passenger seat 12 stops.

This point corresponds to point B in FIG. However, when the load of the hydraulic elevator or the temperature of the oil changes, the flow control valve 6
Since the flow rate characteristics of 1 and 12 change, the speed characteristics of 1st and 12th power change. In other words, the acceleration/deceleration, the speed during full-speed running, or during landing-on-floor running change. An example is shown in FIG.

When the load or oil temperature changes compared to the target speed characteristic shown by the solid line, the speed characteristic becomes the two-dot chain line. In this way, the time taken to travel at the landing speed changes from T- to T-. If T- is long, passengers may feel that the doors will not open even though the elevator has finished decelerating, which may cause irritation. This tendency increases as the range of change in load or oil temperature increases.

The implantation travel time (T,) may vary depending on various conditions.
The present invention is provided with an arithmetic control device 5 that drives the electromagnetic control valve 4 by a command signal from the control command device 1. , the deceleration start command is delayed by the deceleration delay time Δt according to the oil temperature condition and the load condition, and the landing travel time T
, 2 is shortened to T, 3, so that T 處3 = T silver''.

That is, as shown in detail in FIG. 4, a plurality of deceleration delay times Δt are stored in advance in a tabulated memory 17 of the arithmetic and control unit 5 in correspondence with the oil temperature T and the load P.
The oil temperature T detected by the detectors 7 and 8 in response to the start command from the start switch 18 and the start command signal generator 19
The memory 1 stores the deceleration delay time Δt according to the value of the load P.
7 is detected by searchers 15 and 16. When a deceleration command signal is input from the deceleration command signal generator 20 of the control command device 1, the arithmetic and control device 5 delays the deceleration command by the deceleration delay time Δt and operates the electromagnetic control valve 4. In this way, the landing travel time can be shortened from T.2 to T-.

Next, the operation of the elevator of the present invention will be explained by taking an example of a rising operation.

First, when the start switch 18 is turned on, a start command signal from the start command signal generator 19 causes the solenoid Ul of the electromagnetic control valve 4 to be activated via the drive device 22.

U2 is activated. Therefore, the passenger shaft 12 starts to move upward by the pressure oil from the upward flow rate control valve 6. At this time, the oil fA is
T and load P are detected by detectors 7 and 8. According to the detected oil temperature T and the magnitude of the load P, the deceleration delay time Δt is retrieved from the memory 17 by the retrieval units 15 and 16.

On the other hand, when the passenger car 12 accelerates and runs at full speed and switches the deceleration start switch 13 in accordance with the deceleration start position, a deceleration command signal from the deceleration command signal generator 20 is supplied to the drive unit fn23, and from this signal the After a delay of deceleration delay time Δt, the solenoid U1 of the electromagnetic control valve 4 is deenergized. By releasing the solenoid U1, the flow control valve 6 reduces the supply of pressure oil to the hydraulic cylinder. As a result, the passenger car 12 decelerates and travels at the landing speed. When the switch 14 provided at the stop position of the car 12 is switched, a stop command signal from the stop command signal generator 21 is supplied to the drive device 24, and the solenoid U2 of the electromagnetic control valve 4 is deenergized and the car 12 is moved to the stop position. to stop.

Here, the deceleration delay time Δt stored in the tabulated memory 17 depends on the characteristics of the flow control valve 6, and this deceleration delay time Δt is determined as follows.

As shown in Fig. 5, the oil temperature T and load P range of the hydraulic elevator are appropriately divided into a plurality of regions, for example, the load P is divided into m divisions from the minimum load Pln to the maximum load PII&X, and the oil temperature T is From minimum oil temperature T m s n to maximum oil temperature Ta
ll! Up to n divisions. In each of these areas, an appropriate deceleration delay time Δt is stored in advance as an initial value. This Δt is a value determined in advance from the current control characteristics, taking into account variations in each flow rate control valve. If this Δt is an optimal value for the hydraulic elevator system, it is possible to set the landing time T a 3=T * ”.

Due to differences in the specifications of the hydraulic elevators or variations in the flow rate control valves 6, different hydraulic elevators may store different values of Δt even if the areas in the storage device 17 are the same. If the value of Δt is different, Δt is corrected as follows.

That is, the value initially set in the storage device 17 is a value slightly smaller than the greatest common divisor value for various cases. In some cases, the minimum value may be stored.

The value of Δt set in this way and stored in the storage device 17 is
If the value is optimal for the hydraulic elevator as a system, the floor landing travel time T1 can be kept constant using this Δt.

However, there is no guarantee that Δt will always be the optimal value, so in such a case, Δt stored in the memory 17 is corrected as follows.

First, the full speed running speed Vt and the landing running speed Vt.

The deceleration time T1 is stored in the calculator 25 as a linear or quadratic formula as a function of the load P and the oil temperature T. At this time, in order to set the magnitude of the deceleration delay time after correction to the safe side. Then, the full-speed running speed Vt and the deceleration time Tl are the maximum expected values, and the landing running speed ■ is the minimum expected value. Using the detected values of the temperature and load detectors 7 and 8, the computing unit 25 determines the full speed running speed Vt corresponding to the operating conditions.
g The landing speed Va and deceleration time T1 are calculated using the above functions. Further, the time difference T2 between the deceleration start point A and the stop point B is calculated by the calculator 25. This time difference T2 can be obtained by detecting the signal from the deceleration command generator 20 and the signal from the stop command generator 21 using a timer or the like. Therefore, although it is not an actual measurement value, T turtle = T z
-T t allows the actual landing travel time T shift to be estimated.

Therefore, for the target value T- of the landing time, ■.

The delay time Δtej of the (ij) region used will be ΔtIJ next time with respect to the delay time ΔtiJ of Δtsa, and the landing travel time T will approach the target value T t O in the next operation.

By doing so, the deceleration delay time Δt stored in the memory 17 each time the hydraulic elevator is operated becomes more accurate. The search for the deceleration delay time Δt and the calculation for the correction value of Δt are performed while the hydraulic elevator is running, but the calculation takes a very short time. However, in an emergency, only the search for Δt is performed.

Therefore, when the elevator is stopped, the computing unit can perform other tasks such as searching for calls, opening and closing doors, etc., which is very economical.

In the above-described embodiment, oil temperature and load are detected, but of course, if there is little variation, only one of oil temperature or load may be detected. Further, although the load is detected directly from the seat 12, the same effect can be achieved by using the oil pressure of the hydraulic cylinder 9.

〔Effect of the invention〕

According to the present invention, it is possible to significantly reduce the range of variation in the flooring travel time of a hydraulic elevator depending on the load or oil temperature, so that a hydraulic elevator with good riding comfort can be achieved by keeping the traveling time at the flooring traveling speed constant. is obtained.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing an overview of the control system in the hydraulic elevator of the present invention, FIG. 2 is a configuration diagram of the electromagnetic control valve shown in FIG. 1,
Fig. 3 is a characteristic diagram showing each speed characteristic with respect to the load of the rider, Fig. 4 is a configuration diagram of the arithmetic and control unit shown in Fig. 1, and Fig. 5 is a diagram for explaining the tabulation of delay time Δt. be. 1... Control command device, 4... Solenoid control valve, 5...
Arithmetic control device, 6...Flow rate control valve, 7...Oil temperature detector, 8...Load detector, 9...Hydraulic cylinder, 9'
... Plunger, 12 ... Car, 13, 14, 1
3', 14'...switch, Ul, U2. Di, D
2...Solenoid, 15.16...Search device, 17.
...Storage device, 25... Arithmetic unit. ~, 7. Second Ward Condolence 3I! 1 Not 4 [ [ "Knee 1 [-

Claims (1)

[Claims] 1. In a hydraulic elevator in which a car is raised and lowered by a hydraulic device including a hydraulic cylinder and a flow rate control valve, and when landing on the floor, the car is decelerated from a predetermined deceleration start point and travels at a low landing speed. , means for determining a floor landing travel time during which the hydraulic elevator travels at a floor landing speed, a storage means for storing calculation elements for calculating a deceleration delay time for delaying the start of deceleration from the deceleration start point, and the floor landing means. a correction means for determining the difference between the running time and a predetermined target value of the floor landing running time, and correcting the calculation element according to the calculated difference, and adjusting the calculation element stored in the storage means. means for updating the deceleration delay time to the deceleration delay time corrected by the correcting means; and an output means for outputting a command to delay the start of deceleration by the deceleration delay time calculated from the calculation element from the deceleration start point, A hydraulic elevator characterized in that the deceleration of the hydraulic device is controlled by an output from the means. 2. In claim 1, the means for determining the landing travel time determines the floor landing travel time using at least one of the load and oil temperature of the hydraulic system. Hydraulic elevator. 3. The hydraulic elevator according to claim 1, wherein the storage means stores a plurality of deceleration delay times corresponding to the load and oil temperature of the hydraulic system. 4. The hydraulic elevator according to claim 1, wherein the storage means stores a plurality of deceleration delay times corresponding to only one of the load and oil temperature of the hydraulic system.