JP3259506B2 - Drive control device for hydraulic elevator - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive control device for a hydraulic elevator, for example, a drive of a hydraulic elevator of a type in which a hydraulic pump is driven by a motor controlled at a variable speed to send hydraulic pressure to a hydraulic jack and a car is run. The present invention relates to a control device.

[0002]

2. Description of the Related Art In a conventional hydraulic elevator drive control device, an electric motor is rotated at a constant speed when a car rises,
Of the fixed amount of oil discharged from the hydraulic pump, the amount of oil sent to the hydraulic jack is adjusted by the flow control valve, and when the car descends, the oil returns from the hydraulic jack to the tank by the weight of the car. The running speed of each car is controlled by adjusting the amount by the flow control valve. This method has a large energy loss for returning an excess oil amount from the hydraulic pump to the tank during the ascending operation, and a large increase in the oil temperature for converting potential energy into heat during the descending operation.

On the other hand, recently, an induction motor is controlled by a variable voltage and a variable frequency (hereinafter referred to as VVV) using an inverter or the like.
A method of variably controlling the discharge amount of a pump driven by an induction motor by controlling the speed by F control) has been proposed. In this method, only the required oil amount is sent to the hydraulic jack in accordance with the speed command value during the ascending operation, and the electric motor is regeneratively braked by the amount of oil flowing back to the tank during the descending operation. , And a highly efficient hydraulic elevator can be obtained.

Incidentally, in the VVVF control hydraulic elevator, the electromagnetic switching valve for opening and closing the flow path of the pressure oil may be simply opened or closed, but at the same time as rotating the induction motor at the time of starting the elevator, When the solenoid-operated directional control valve is opened, the car is lowered because the pump side pressure is lower than the jack side pressure, and a large starting shock and vibration are generated. On the other hand, for example, Japanese Unexamined Patent Publication No. Hei.
As disclosed in Japanese Patent Application Laid-Open No. 6-206, a pressure sensor for detecting jack-side pressure and pump-side pressure is provided to control the torque of the electric motor in response to the deviation, and to control the speed based on the output of the pressure controller. It has been proposed that the jack side pressure and the pump side pressure are made equal by calculating a command value, and the starting shock is suppressed by running the car. FIG. 11 shows a configuration diagram of this conventional drive control device for a hydraulic elevator. In the figure, reference numeral 1 denotes a cylinder installed in a pit of a hoistway, 2 denotes a pressure oil filled in the cylinder 1, 3 denotes a plunger supported by the pressure oil 2, and 1 to 3 constitute a hydraulic jack. I do. Also, 4
Is a deflecting car attached to the top of the plunger 3, 5 is a rope attached to the deflecting car 4 with one end fixed to the pit, 6 is a basket attached to the other end of the rope 5, and 7 is always functioning as a check valve An electromagnetic switching valve, which is switched by being energized by the electromagnetic coil to conduct in the reverse direction, 8
Is a pipe connected between the cylinder 1 and the electromagnetic switching valve 7 to send pressure oil, 9 is a hydraulic pump that operates reversibly and sends and receives oil pressure to and from the electromagnetic switching valve 7 through the pipe 10, 11 is oil, Reference numeral 12 denotes an oil tank in which oil 11 is stored, which sends and receives oil to and from the hydraulic pump 9 via a pipe 13. Reference numeral 14 denotes a three-phase induction motor IM that drives the hydraulic pump 9,
Give to. A speed detector 15 detects the number of revolutions of the induction motor 14 and outputs a voltage proportional to the number of revolutions of the induction motor 14. 16 is a jack-side pressure sensor for detecting the pressure in the pipe 8; 17 is a pump-side pressure sensor for detecting the pressure in the pipe 10; 18 is a three-phase AC source;
Is a converter for converting three-phase AC to DC, 20 is a smoothing capacitor for smoothing the output of the converter 19, 21 is a regenerative resistor for consuming regenerative power, and 22 is a regenerative transistor that conducts when in a regenerative state. , 23 are inverters for driving the induction motor 14, 24 is a pressure controller PC to which the outputs of the sensors 16, 17 are supplied, 25
Is an adder for adding the output of the pressure balance speed command calculator 31 and the car traveling pattern command 26, and 27 is a speed controller S to which the output of the adder 25 and the output of the speed detector 15 are supplied.
C and 28 are current detectors for detecting the input current of the induction motor 14, 29 is a torque controller VC that controls the inverter 23 according to the outputs of the current detector 28, the speed detector 15 and the adder 30, Reference numeral 30 denotes an adder for adding the output of the speed controller 27 and the output of the pressure controller 24, and 31 has a transfer function having an inverse characteristic to the transfer function of the speed controller 27, and according to the output of the pressure controller 24, A pressure balance speed command calculator PBSP that calculates a pressure balance speed command that invalidates the DC component of the deviation from the output of the speed detector 15.

Next, the operation will be described with reference to the drawings. Now, if the car 6 is called, the jack-side pressure sensor 16
And the value of the pump-side pressure sensor 17 are
Is input to The output is input to the torque controller 29 via the adder 30. The torque controller 29 drives the inverter 23 by the output of the pressure controller 24, the output of the speed detector 15, and the output of the current detector 28, and the inverter 23 drives the induction motor 14. Then, the pressure controller 24 automatically adjusts the pressure balance torque command input to the torque controller 29 so that the output deviation between the jack side pressure sensor 16 and the pump side pressure sensor 17 becomes zero. At this time, the induction motor 14 rotates, but the pressure balance torque command is converted to the pressure balance speed command calculator 31.
, The pressure balance speed command calculator 31 automatically calculates a speed command value that is substantially proportional to the pressure balance torque command and inputs the speed command value to the speed controller 27. The DC component of the deviation from the output of the motor 15 becomes smaller, and the running pattern command 26 is not output, so that the torque command output by the speed controller 27 to stop the induction motor 14 is also reduced. I do. In this way, the jack side pressure and the pump side pressure become equal. After the pressures are equalized, the electromagnetic switching valve 7
open. At this time, the hydraulic jack does not move because the jack side pressure and the pump side pressure are equal. Of course, the basket does not move either. Then, the induction motor 14 is driven by the car traveling pattern command 26 to move the car 6 up and down. At this time, the pressure controller 24 is not operated, and the pressure balance torque command when the pressure is balanced and the output value of the pressure balance speed command calculator 31 at that time are stored, and the values are stored in the torque controller 29 and the speed control, respectively. Input to the container 27.

Since the conventional technique is configured as described above, the output of the pressure balance speed command calculator 31 is determined only by the value of the pressure balance torque command. That is, the jack-side pressure sensor 1 output by the pressure controller 24
The value of the pressure balance torque command that makes the output deviation of the pressure sensor 6 and the pump side pressure sensor 17 zero is almost the same even at a high temperature as at a low temperature.
The output of 1 is the same both at high and low temperatures. That is,
When the oil temperature becomes high, the leakage of the hydraulic pump 9 increases, so that the pressure balance speed command output by the pressure balance speed command calculator 31 becomes relatively small. As a result, the torque command output by the speed controller 27 to stop the induction motor 14 increases, and the time until the jack side pressure and the pump side pressure become equal becomes longer. If the gain of the pressure controller 24 is set to be larger than the gain of the speed controller 27, the jack-side pressure and the pump-side pressure eventually become equal. However, when the oil temperature becomes higher, the jack-side pressure becomes lower than the jack-side pressure. There is a problem that the time required for the pump side pressures to be equal becomes longer.

[0007]

A compensation torque for compensating for the pressure difference between the pump side pressure and the jack side pressure is applied to the input of the torque controller, and the pressure balance speed command calculated from the compensation torque at this time is subjected to speed control. The pressure balance speed command output from the pressure balance speed command calculator becomes relatively small due to the increase in pump leakage at high temperatures when the temperature is high. However, the torque command output by the speed controller to stop the induction motor becomes large, and the time until the jack side pressure becomes equal to the pump side pressure becomes longer, and the response until the car is started is delayed. .

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and a first object of the invention is to quickly change the pump side pressure to the jack side pressure with little change in response time between a low temperature and a high temperature. It is an object of the present invention to provide a hydraulic elevator drive control device that can be equalized.

A second object of the present invention is to provide a hydraulic elevator drive control device capable of suppressing an overshoot after the pump side pressure reaches the jack side pressure and enabling a smooth start of the car. A third object is to provide a drive control device for a hydraulic elevator that can prevent an abnormal increase in the pump side pressure or the rotation speed of the electric motor. Also,
A fourth object is to provide a drive control device for a hydraulic elevator in which the pump-side pressure is prevented from rising above the jack-side pressure when the car descends, and the operation of the solenoid valve is stable.

[0010]

SUMMARY OF THE INVENTION A drive control device for a hydraulic elevator according to the present invention comprises an electric motor for driving a hydraulic pump for sending hydraulic oil to a hydraulic jack for raising and lowering a car, and a speed detector for detecting the speed of the electric motor. A current detector for detecting the operating current of the electric motor, a solenoid valve for preventing the flow of the hydraulic oil, a pump-side pressure detector for detecting the hydraulic pump-side hydraulic pressure, and a jack for detecting the hydraulic jack-side hydraulic pressure A side pressure detector, a pressure controller that outputs a deviation signal corresponding to an output difference between the pump side pressure detector and the jack side pressure detector, a speed command value for running the car, an output of the speed detector, and an adder. a speed controller for outputting a torque command value corresponding to the output, based on the output of the torque command value and the deviation signal and the current detector and the speed detector, the motor system for controlling the electric motor A torque controller for outputting the compensation torque command value to reduce the output deviation in the vessel, the torque command
Output a command value that makes the torque command value zero based on the value
Pressure balance speed command calculator and the output of the speed detector
A differential operation unit for differentiating the force, wherein the adder is:
Output of the differential calculator and the pressure balance speed command calculator
And outputs a signal to the speed controller .

[0011] Also, the drive control system for a hydraulic elevator according to the invention, obtains a reference value from the output of the jack side pressure detector, holding circuit the reference value and outputs it to the pressure controller as an output of the jack side pressure detector It is provided with.

Further, the drive control apparatus for a hydraulic elevator according to the present invention obtains a reference value from the output of the jack-side pressure detector, and outputs a step-like signal that uses the reference value as the output of the jack-side pressure detector. A circuit and a first-order lag filter for dulling the step-like signal and outputting it to the pressure controller.

Further, the drive control device for a hydraulic elevator according to the present invention includes a pressure limiter that regulates an upper limit of an output value of the pressure controller.

Further, the drive control device for a hydraulic elevator according to the present invention is provided with a speed limiter for regulating an upper limit of an output value of the pressure balance speed command calculator.

The drive control device for a hydraulic elevator according to the present invention compares the output ratio of the pump-side pressure detector to the jack-side pressure detector, and shifts to the running pattern when the output ratio exceeds a predetermined value. And a first comparison circuit for outputting a signal to be output.

Further, the drive control device for a hydraulic elevator according to the present invention compares the output ratio of the pump-side pressure detector to the jack-side pressure detector, and when the output ratio is less than a predetermined value within a predetermined time, the travel pattern is determined. And a second comparison circuit for outputting a signal for stopping the shift to the negative side.

Further, the drive control device for a hydraulic elevator according to the present invention stores the command value of the pressure balance speed command calculator when the outputs of the pump side pressure detector and the jack side pressure detector are balanced before the car is started. After landing on the storage device and the car, the command value is reduced according to the descent of the car,
And a pressure balance speed command subtraction circuit for outputting to the speed controller.

Further, the drive control device for a hydraulic elevator according to the present invention compares the output ratio of the pump-side pressure detector to the jack-side pressure detector, and when the output ratio exceeds a predetermined value within a predetermined time, the travel pattern 3. The driving device for a hydraulic elevator according to claim 1, further comprising a third comparison circuit that outputs a signal that shifts to a negative state.

[0019]

According to the present invention, there is provided a hydraulic elevator drive control device comprising: a differential operation unit for differentiating an output of a speed detector;
An adder that calculates the output of the differential calculator and the command value of the pressure balance speed command calculator and outputs a signal to the speed controller is provided, so that the differential calculator suppresses fluctuations in the rotation speed of the motor and In addition, the overshoot after the pump side pressure is increased to the jack side pressure is suppressed.

Further, the drive control device for a hydraulic elevator according to the present invention includes a holding circuit for obtaining a reference value from the output of the jack side pressure detector and outputting the reference value to the pressure controller. The output of the vessel is considered to be constant during the pressure control, and is not affected by fluctuations in the jack side pressure due to the swinging of the car.

Further, the drive control apparatus for a hydraulic elevator according to the present invention obtains a reference value from the output of the jack side pressure detector, and outputs a reference value as a step signal, a holding circuit, and a step signal for dulling the step signal. And a first-order lag filter that outputs to the pressure controller.
The pump-side pressure is not easily influenced by the fluctuation of the jack-side pressure due to the swinging of the car and the like, and the pump-side pressure easily follows the jack-side pressure. Therefore, the overshoot after the pump-side pressure has increased to the jack-side pressure is suppressed.

Further, the drive control device of the hydraulic elevator according to the present invention is provided with a pressure limiter for regulating the upper limit of the output value of the pressure controller. Suppress abnormally high pump side pressure.

Further, the drive control device of the hydraulic elevator according to the present invention is provided with a speed limiter for regulating the upper limit of the output value of the pressure balance speed command calculator, and the speed limiter leaks due to a failure of the electromagnetic switching valve or the like. Prevent the motor from rotating at an abnormally high speed when the flow rate is abnormally high.

Further, the drive control device of the hydraulic elevator according to the present invention compares the output ratio of the pump side pressure detector with respect to the jack side pressure detector and, when the output ratio exceeds a predetermined value, shifts to a traveling pattern. The traveling is started before the hydraulic pump side pressure reaches the hydraulic jack side pressure.

Further, in the drive control apparatus for a hydraulic elevator according to the present invention, after the pressure control is started, the second comparison circuit
The output ratio of the pump-side pressure detector to the jack-side pressure detector is compared. If the output ratio is less than a predetermined value within a predetermined time, a signal is output to stop shifting to the running pattern, and the running is stopped. .

Further, the drive control apparatus for a hydraulic elevator according to the present invention stores the command value of the pressure balance speed command calculator when the outputs of the pump side pressure detector and the jack side pressure detector are balanced before the car is started. The apparatus has a pressure balance speed command subtraction circuit, which reduces the command value of the pressure balance speed command calculator according to the descent of the car after landing on the car and outputs the command value to the speed controller. The pressure does not exceed the hydraulic jack pressure.

Further, the drive control apparatus for a hydraulic elevator according to the present invention compares the output ratio of the pump side pressure detector to the jack side pressure detector, and when the output ratio becomes equal to or greater than a predetermined value within a predetermined time, the travel pattern. Since the third comparison circuit for outputting the signal for shifting to the condition (1) is provided, the vehicle starts running before the hydraulic pump side pressure reaches the hydraulic jack side pressure.

[0028]

[Embodiment 1] An embodiment of the present invention will be described below with reference to the drawings. FIG.
FIG. 1 is a configuration diagram showing one embodiment of the present invention. In the figure, FIG.
The same reference numerals as 1 denote the same or corresponding parts, and a description thereof will be omitted. In the figure, reference numeral 32 denotes a differential operation unit for differentiating the output of the speed detector 15, and 33 denotes a speed controller 27 from 0 input.
The subtractor 34 calculates the value at which the output of the subtractor 33 is supplied and the output of the speed controller 27 becomes zero.
A pressure balance speed command calculator that outputs the value to the speed controller 27, 35 is an adder that adds the outputs of the differential calculator 32 and the pressure balance speed command calculator 34, and 36 is an adder 3
5 is added to the car traveling pattern command 26; 37 is an adder for adding the output of the speed controller 27 and the output of the pressure controller 24; and 46 to 49 are coils (not shown) only at the time of startup. Are the contacts of the relay that are excited and closed.

Next, the operation of the embodiment of the present invention will be described with reference to the drawings. Assuming that the car 6 is called, the coil (not shown) of the relay is excited, and the contacts 46 to 49 are closed. Next, the value of the jack-side pressure sensor 16 and the value of the pump-side pressure sensor 17 are input to the pressure controller 24, and the pressure difference between the oil pressures of the sensors 16, 17 is output as a deviation signal. The output is input to the torque controller 29 via the adder 37. The torque controller 29 outputs the output of the pressure controller 24, the output of the speed controller 27, and the output of the current detector 28 to the inverter 23 which is a motor controller.
, And the inverter 23 drives the induction motor 14. Then, the pressure controller 24 automatically adjusts the value input to the torque controller 29 so that the output deviation between the jack-side pressure sensor 16 and the pump-side pressure sensor 17 becomes zero. At this time, although the induction motor 14 rotates, the speed controller 27 attempts to stop the induction motor 14 because the traveling pattern signal 26 is not output, so that the output of the speed controller 27 becomes zero. The pressure balance speed command calculator 33 automatically adjusts the value input to the speed controller 27 so as to satisfy the following. Since this value is adjusted so that the output of the speed controller 27 becomes zero, even if the leakage flow rate of the pump 9 increases due to an increase in the oil temperature, the output of the pressure balance speed command calculator 33 will be the speed at that time. The output of the speed detector 15 becomes zero because the output becomes almost the same as the output of the detector 15, and the output of the speed detector 15 does not operate to stop the induction motor 14. There is no response delay. That is, the pressure balance speed command calculator 33 operates to prevent the operation of the speed controller 27. Further, the speed detector 15 is operated by the differential calculator 32.
Is calculated, added to the output of the pressure balance speed command calculator 34 by the adder 35, and input to the speed controller 27. The output of the adder 35 is the sum of the value calculated so that the output of the speed controller 27 becomes zero and the rotational acceleration of the induction motor 14 which is a differential value by the differential calculator 32. The output is kept at almost zero except for suppressing the speed fluctuation of the induction motor 14 due to the differential value, so that the speed controller 27 does not work to stop the induction motor 14.

In this way, the jack pressure and the pump pressure become equal. After the pressures become equal, the coil of the relay is demagnetized and the contacts 46 to 49 are opened. At this time, the pressure controller 24, the differential calculator 32, and the pressure balance speed command calculator 34 are not operated, and respective output values when the pressure is balanced are stored in a storage device (not shown). Are the torque controller 29 and the speed controller 2 respectively.
7 to open the electromagnetic switching valve 7. At this time, the hydraulic jack does not move because the jack side pressure and the pump side pressure are equal. Of course, the car 6 does not move either. then,
The induction motor 14 is driven by the car speed command 26 to move the car 6 up and down.

As described above, since the pressure balance speed command calculator 34 makes the output of the speed controller 27 zero, the value that makes the deviation between the jack side pressure and the pump side pressure zero is obtained from the pressure controller 24. Output to the torque controller 29. The pump-side pressure can be quickly made equal to the jack-side pressure without being affected by an increase in pump leakage due to a change in oil temperature. Further, the differential calculator 32 suppresses sudden speed fluctuation of the induction motor 14 and suppresses overshoot after the pump side pressure reaches the jack side pressure, so that the pump is opened when the electromagnetic switching valve 7 is opened. The side pressure becomes equal to the jack side pressure, and the overpressure of the pump side pressure
The shock of the car due to ト is reduced. Further, since the pressure balance speed command calculator 33 operates to prevent the operation of the speed controller 27, the speed controller 2
It is considered that the operation of step 7 is unnecessary. However, if the speed controller 27 is suddenly operated by the traveling pattern command 26 at the end of the pressure control, a car shock occurs.
The operation pattern is shifted from the state in which is operated to the traveling pattern. Further, the induction motor 14 is driven by the traveling pattern command 26 to move the car 6 up and down. At this time, the pressure controller 24 is not operated, and the output value of the pressure controller 24 when the pressures are balanced is determined. The output value of the pressure balance speed command calculator 34 at that time is stored, and the value is input to the torque controller 29 and the speed controller 27, respectively. In this case, if the pressure controller 24 is operated when the electromagnetic switching valve 7 is closed, for example, the car 6 can be immediately moved by the liberal pattern signal even in the case of the liberal operation or the like.

Embodiment 2 FIG. FIG. 2 is a block diagram showing an embodiment of another aspect of the present invention. In the figure, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will not be repeated. In the figure, the output of the jack-side pressure sensor 16 immediately before startup holds a reference value that corrects the fluctuation of the jack-side pressure generated by the passenger getting on and off the car, and outputs the reference value to the pressure controller 24. 3
8 are provided. Here, the pressure controller 24 automatically adjusts the value input to the torque controller 29 so that the output deviation between the jack-side pressure sensor 16 and the pump-side pressure sensor 17 becomes zero. At the time of control, if the car fluctuates due to the car being shaken due to the passenger getting on / off or moving in the car, the pressure control becomes unstable. In order to prevent such a problem, the holding circuit 38 stores the output of the jack-side pressure sensor 16 several times during the predetermined period during which the car is closed, after the passengers have finished getting on and off, and averages the output. It is held as a reference value, and this reference value is
To avoid the effect of fluctuations in jack-side pressure caused by output to the jack.

Embodiment 3 FIG. FIG. 3 is a block diagram showing an embodiment of another aspect of the present invention. In the drawing, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will not be repeated. In the figure, a first-order lag filter 39 is provided on the output side of a holding circuit 38. With this configuration, the reference value held by the holding circuit 38 is output as a step-like signal. However, the reference value is added to the pressure controller 24 as a signal whose rising edge is dull by the first-order lag filter 39. It becomes easy to follow the jack-side pressure of the signal whose rise is dull, and it is possible to suppress the overshoot after the pressure is raised to a value equal to the jack-side pressure.

Embodiment 4 FIG. FIG. 4 is a block diagram showing an embodiment of another aspect of the present invention, in which the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will be omitted. In the figure, a pressure limiter 40 is provided on the output side of the pressure controller 24 for suppressing the output of the pressure controller 24 from exceeding a predetermined value. With this configuration, the pressure transmitter 40 suppresses the output of the pressure controller 24 from becoming equal to or more than the predetermined value. Therefore, the failure of the jack-side pressure sensor 16 and the pump-side pressure sensor 17 that are power sensors causes the pressure controller 24 It is possible to prevent the output from increasing abnormally and the actual hydraulic pump side pressure from increasing abnormally, leading to unsafe operation.

Embodiment 5 FIG. FIG. 5 is a block diagram showing an embodiment of another aspect of the present invention. In the figure, the same reference numerals as those in FIG. In the figure, a speed limiter 41 that regulates the upper limit of the output of the adder 35 is provided on the output side of the adder 35. With this configuration, when the leakage flow rate becomes abnormally large due to the failure of the electromagnetic switching valve 7 or the like, the speed limiter 41 limits the output to the speed controller 27, so that the speed controller 27 decelerates the induction motor 14. In order to compensate for the leakage flow rate, the induction motor 14 can be prevented from rotating at a dangerous rotation speed exceeding the rated rotation speed. In this embodiment, the limiter 41 is provided on the output side of the adder 35.
The same effect can be obtained even if the speed limiter 41 is provided on the output side.

Embodiment 6 FIG. FIG. 6 is a block diagram showing an embodiment of another aspect of the present invention, in which the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will be omitted. FIG. 10 is an explanatory diagram illustrating the relationship between time and pump-side pressure, with the horizontal axis representing time and the vertical axis representing pump-side pressure value. In the figure, a comparison circuit 42 which is a first comparison circuit for comparing the outputs of the jack side pressure sensor 16 and the pump side pressure sensor 17 is provided.
Is input to a circuit (not shown) for generating a traveling pattern command 26. The pump-side pressure is preset with respect to the jack-side pressure by the comparison circuit 42.
As soon as the first set value shown in FIG. 10 is reached, the mode can be shifted to the car running mode, and the dead time from the start to the actual running of the car can be minimized. This first set value is usually set between 90% and 100% of the jack pressure. In this case, since the pump side pressure does not increase to the jack side pressure, a car shock at the time of startup occurs. Wasted time is kept to a minimum.

Embodiment 7 FIG. FIG. 7 is a block diagram showing an embodiment of another aspect of the present invention. In the drawing, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will not be repeated. In the figure, a third comparison is made between the outputs of the jack-side pressure sensor 16 and the pump-side pressure sensor 17.
A comparison circuit 42A is provided.
The output of A is input to a circuit for generating a traveling pattern command 26, and a timer 43 for measuring the time during pressure control from the start.
Is provided. It takes time for the pump 43 pressure to reach the first set value shown in FIG. 10 due to some abnormality due to the timer 43, and before the waste time from the start to the actual running of the car becomes unnecessarily long, FIG.
When the hydraulic pump side pressure has reached the second set value shown in FIG. 10 when the first set time shown in FIG. 10 has been reached, the comparison circuit 42A outputs a command to shift to the car running mode. In addition, the dead time from the start to the actual running of the car can be minimized. Normally, the second set value is set to a value lower than the first set value, and a car shock at the time of starting due to the hydraulic pump side pressure not reaching the hydraulic jack side pressure is allowed for passenger safety. Is selected. The time required for the normal hydraulic pump side pressure to reach the hydraulic jack side pressure is 0.4 to 0.6 sec.
Therefore, the first set time is set to about 1 sec.

Embodiment 8 FIG. FIG. 8 is a block diagram showing an embodiment of another aspect of the present invention. In the drawing, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will not be repeated. In the figure, a comparison circuit 42B, which is a second comparison circuit, and an abnormality detection circuit 44 that operates by the output of the timer 43A are provided. This abnormality detection circuit 44
When the output of the timer 43A reaches the preset second set time shown in FIG. 10 and the comparison circuit 42B detects that the pump side pressure has not reached the second set value shown in FIG. Abnormal operation of the elevator is prevented by detecting the pressure, stopping the pressure control and making it impossible to restart the elevator.

Embodiment 9 FIG. FIG. 9 is a block diagram showing an embodiment of another aspect of the present invention. In the drawing, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and a description thereof will not be repeated. In the figure, there is provided a pressure balance speed command subtraction circuit 45 for gradually decreasing the pressure balance speed command stored in the storage device at the time of pressure control of the operation when the car descends. The pressure balance speed command subtraction circuit 45 gradually decreases the pressure balance speed command stored during the pressure control of the operation after the landing of the elevator and outputs the reduced pressure balance speed command to the speed controller 27. The pressure difference due to the floor, especially when traveling from the top floor to the lowest floor, the jack-side pressure after landing is lower than the jack-side pressure before traveling. With the values held by the pressure controller 24 and the pressure balance speed command calculator 34, the phenomenon that the pump side pressure becomes higher than the jack side pressure and the electromagnetic switching valve 7 becomes difficult to close can be prevented. The reliability of the elevator driving device is improved.

[0040]

As is evident from the foregoing description, according to the present invention, by calculating a differential calculator for differential operation the output of the velocity detector, a command value of the output and the pressure balance speed command calculator differential calculator When an adder that outputs a signal to the speed controller is provided, abrupt fluctuation of the rotation speed of the electric motor is suppressed, and
There is an effect that a drive control device for a hydraulic elevator that can suppress an overshoot after the pump-side pressure has increased to the jack-side pressure and suppress a shock at the start of traveling and a vibration accompanying the same can be obtained.

According to the next invention, when a reference value is obtained from the output of the jack-side pressure detector and a holding circuit for outputting the reference value to the pressure controller is provided, an apparent jack due to car rocking or the like is provided. There is an effect that a drive control device for a hydraulic elevator that operates stably without being affected by the fluctuation of the side pressure is obtained.

According to the next invention, a reference circuit is determined from the output of the jack-side pressure detector, and a holding circuit for outputting the reference value as a step signal is provided. The output of the first-order lag filter is not affected by the fluctuation of the apparent jack-side pressure due to car shaking or the like, and the pump-side pressure can follow the output of the first-order lag filter. There is an effect that a drive control device for a hydraulic elevator that can suppress an overshoot after the pressure has been raised to the jack-side pressure and suppress a shock at the start of traveling and a vibration accompanying the same can be obtained.

According to the next invention, when a pressure limiter for regulating the upper limit of the output value of the pressure controller is provided, the pump-side pressure becomes abnormally high when an abnormality such as a failure of the pump pressure detector occurs. Thus, there is an effect that a drive control device for a hydraulic elevator that operates stably can be obtained.

According to the next invention, if a speed limiter for regulating the upper limit of the output value of the pressure balance speed command calculator is provided, the motor is operated when the leakage flow rate is abnormally large due to a failure of the electromagnetic switching valve or the like. Is suppressed from rotating at an abnormally high speed, and a drive control device for a hydraulic elevator that operates stably can be obtained.

According to the next invention, the output ratio of the pump-side pressure detector to the jack-side pressure detector is compared, and when the output ratio exceeds a predetermined value, a signal for shifting to the traveling pattern is output. If the first comparison circuit is provided, the traveling starts before the output of the pump-side pressure detector reaches the output of the jack-side pressure detector. Therefore, the hydraulic elevator capable of shifting to the car traveling while minimizing the dead time is provided. This is effective in obtaining the drive control device described above.

According to the next invention, after the start of the pressure control, the second comparison circuit compares the output ratio of the pump side pressure detector with respect to the jack side pressure detector, and the output ratio becomes a predetermined value within a predetermined time. If a signal to stop the shift to the running pattern is output if the condition is not satisfied, and the running is stopped, it is possible to detect an abnormality before running the car and prevent unsafe operation before running the car in case of any equipment abnormality. Thus, there is an effect that a drive control device for a hydraulic elevator that can be operated is obtained.

Further, according to the next invention, a storage device for storing the command value of the pressure balance speed command calculator when the output of the pump side pressure detector and the output of the jack side pressure detector before the start of the car is balanced, and After landing, the command value of the pressure balance speed command calculator is reduced in accordance with the descent of the car, and a pressure balance speed command subtraction circuit that outputs the command value to the speed controller is provided. Since the pressure does not exceed, the hydraulic valve can be easily closed after landing on the floor irrespective of the pressure difference due to the floor height, and the drive control device of the hydraulic elevator that operates stably can be obtained.

According to the next invention, the output ratio of the pump-side pressure detector to the jack-side pressure detector is compared, and when the output ratio exceeds a predetermined value within a predetermined time, a signal for shifting to a traveling pattern. When the third comparison circuit is provided, the traveling starts before the output of the pump-side pressure detector reaches the output of the jack-side pressure detector. Thus, there is an effect that a drive control device for a hydraulic elevator that can be operated is obtained.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing a hydraulic elevator drive control device including a pressure balance speed command calculator and a differential calculator according to an embodiment of the present invention.

FIG. 2 is a configuration diagram showing a hydraulic elevator including a holding circuit according to an embodiment of the present invention.

FIG. 3 is a configuration diagram showing a drive control device for a hydraulic elevator including a holding circuit and a first-order lag filter according to an embodiment of the present invention.

FIG. 4 is a configuration diagram showing a drive control device of a hydraulic elevator including a pressure limiter according to one embodiment of the present invention.

FIG. 5 is a configuration diagram showing a drive control device of a hydraulic elevator including a speed limiter according to one embodiment of the present invention.

FIG. 6 is a configuration diagram showing a drive control device for a hydraulic elevator including a first comparison circuit according to an embodiment of the present invention.

FIG. 7 is a configuration diagram showing a drive control device of a hydraulic elevator including a second comparison circuit according to an embodiment of the present invention.

FIG. 8 is a configuration diagram showing a drive control device of a hydraulic elevator including an abnormality detection circuit according to one embodiment of the present invention.

FIG. 9 is a configuration diagram showing a drive control device of a hydraulic elevator including a subtraction circuit according to an embodiment of the present invention.

FIG. 10 is an explanatory diagram of changes in the elapsed time of the pressure control and the pressure on the pump side according to the embodiment of the present invention, and the treatment at that time.

FIG. 11 is a configuration diagram showing a conventional drive control device for a hydraulic elevator.

[Explanation of symbols]

 2 Pressure Oil 6 Basket 7 Solenoid Switching Valve 9 Hydraulic Pump 14 Induction Motor 15 Speed Detector 16 Jack-Side Pressure Sensor 17 Pump-Side Pressure Sensor 23 Inverter as Motor Controller 24 Pressure Controller 26 Torque Controller 27 Speed Controller 28 Current Detector 32 Differential calculator 34 Pressure balance speed command calculator 35, 36, 37 Adder 38 Holding circuit 39 Primary delay filter 40 Pressure limiter 41 Speed limiter 42, 42A, 42B Comparison circuit 43 Timer 43A Timer 44 Abnormal Detection circuit 45 Subtraction circuit

Claims (9)

(57) [Claims] An electric motor for driving a hydraulic pump for feeding hydraulic oil to a hydraulic jack for raising and lowering a car; a speed detector for detecting a speed of the electric motor; a current detector for detecting an operation current of the electric motor; A solenoid valve for blocking the flow of pressurized oil, a pump-side pressure detector for detecting the hydraulic pump-side hydraulic pressure, a jack-side pressure detector for detecting the hydraulic jack-side hydraulic pressure, the pump-side pressure detector, and the jack-side pressure detector A pressure controller that outputs a deviation signal corresponding to the output difference of the vehicle, a speed command value for running the car, and an addition of the output of the speed detector
A speed controller for outputting a torque command value according to the output of the vessel, on the basis of the output of the torque command value and the deviation signal and the current detector and the speed detector, the the motor controller for controlling the electric motor A torque controller that outputs a compensation torque command value for reducing the output deviation, and a torque controller based on the torque command value.
To output a command value that makes the torque command value zero.
Balance the output of the speed command calculator and the speed detector
A differential operation unit for performing a differential operation, wherein the adder
Computing unit output and pressure balance speed command Computing unit command
Calculate the value and output a signal to the speed controller.
Motor drive unit - a hydraulic elevator to symptoms. 2. A search of the reference value from the output of the jack side pressure detector, <br/> the reference value in Claim paragraph 1 which includes a holding circuit for outputting the pressure controller as an output of the jack side pressure detector A drive device for the hydraulic elevator according to any one of the preceding claims. 3. A holding circuit for obtaining a reference value from the output of the jack-side pressure detector and outputting a step-like signal using the reference value as the output of the jack-side pressure detector; 3. The hydraulic elevator drive device according to claim 1, further comprising a first-order lag filter that outputs a signal to the pressure controller. 4. The hydraulic elevator according to claim 1, further comprising a pressure limiter that regulates an upper limit of an output value of the pressure controller.
Drive device. 5. the First claims serial <br/> mounting with a speed limiter for restricting the upper limit of the output value of the pressure balance speed command calculator Hydraulic elevator - motor drive. 6. A first comparison circuit for comparing an output ratio of a pump-side pressure detector to a jack-side pressure detector and outputting a signal for shifting to a running pattern when the output ratio exceeds a predetermined value. motor drive unit - a hydraulic elevator of claim 1 wherein the. 7. An output ratio of the pump-side pressure detector to the jack-side pressure detector is compared. If the output ratio is less than a predetermined value within a predetermined time, a signal for stopping a shift to a traveling pattern is output. 2. A first comparison circuit comprising:
A drive device for a hydraulic elevator according to item 13. 8. A storage device for storing a command value of a pressure balance speed command computing unit when outputs of a pump side pressure detector and a jack side pressure detector are balanced before starting a car, and the command value after the car has landed on the car. The value decreases as the car descends,
2. A drive device for a hydraulic elevator according to claim 1, further comprising a pressure balance speed command subtraction circuit for outputting to a speed controller. 9. A third method for comparing the output ratio of the pump-side pressure detector to the jack-side pressure detector and outputting a signal for shifting to the running pattern when the output ratio becomes equal to or greater than a predetermined value within a predetermined time. The drive device for a hydraulic elevator according to claim 1, further comprising a comparison circuit.