JPH075243B2 - Hydraulic elevator valve equipment - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic elevator valve device, and more particularly to a hydraulic control device for controlling an amount of oil from a hydraulic pump or an actuator, which includes a raising control valve and a lowering control valve. However, the present invention relates to a hydraulic elevator valve device that keeps the cage speed at the command value.

[Conventional technology]

As one of elevator drive devices for raising and lowering the cage of an elevator, a hydraulic cylinder is often adopted when the raising and lowering distance of the cage is short. For raising and lowering the cage, one is to directly use the expansion and contraction of the plunger of the hydraulic cylinder, and the other is an indirect type in which a fixed pulley is installed at the upper part of the cage elevating space and a rope is hung on it to increase the expansion and contraction amount of the plunger and raise and lower the cage. There are things.

In any case, by operating an actuator such as a hydraulic cylinder and adjusting the operating speed of the actuator, it is possible to obtain an acceleration, a constant (total) speed and a deceleration operation when the cage moves up and down. The amount of supply and discharge of hydraulic oil is controlled by.

In order to control the amount of oil supplied and discharged from the actuator that directly raises and lowers the cage, a case where a hydraulic pilot system is applied to the raising control valve and the lowering control valve of the elevator valve device,
In some cases, an electric control method is applied. These are equipped with a normally open type ascending control valve and a normally closed type ascending control valve, and control the amount of oil from the hydraulic pump or actuator to keep the cage speed at the command value. .

In the former hydraulic pilot system, the valve bodies of the ascending control valve and the descending control valve are displaced by the pilot pressure. Each hydraulic pilot circuit has an electromagnetic control valve.By turning the electromagnetic control valve on and off based on an elevator up / down command, the amount of oil supplied to the actuator during ascent or the actuator during descent can be adjusted. The amount of oil discharged from the tank is adjusted.

On the other hand, in the latter electric control method, both the raising control valve and the lowering control valve are electromagnetic control valves, and the solenoid is provided with a pre-stored current pattern to change the degree of excitation, so that each control valve directly controls the oil. I try to adjust the amount. Such a latter type of hydraulic elevator valve is described in "Elevator World", Vol. 21, No. 84, page 25, issued by the Japan Elevator Association.

Of the above two types of hydraulic elevator valves, the latter will be taken as an example to explain the control. In the case of raising the cage, when there is a command from the passenger, the hydraulic pump 41 shown in FIG. 34 is driven, and at the same time, for example, from the opening command means 42 such as a microcomputer, a solenoid proportional valve which is a control valve for raising. A signal for exciting the solenoid 43a of 43 is output. The signal has a pattern that initially increases gradually and gradually to increase the supply amount to the actuator 44.

The opening degree of the raising control valve 43 is kept small so that the actuator 44 extends at a constant total speed after a predetermined time has elapsed. When approaching the deceleration position by raising the cage, the deceleration limit switch is actuated, and the lift control valve 43
A signal for weakening the exciting force of the solenoid 43a is output based on the memory pattern so as to gradually increase the opening degree of.
When the landing speed is about 1/8 to / 10 of the full speed, a signal for maintaining the opening for a predetermined time is applied to the solenoid 43a.

When the stop limit switch for floor alignment is activated,
The signal from the opening instruction means 42 is stopped. Such a signal pattern is, for example, as shown in FIG.
It is a constant trapezoidal current waveform Su that realizes constant velocity Vju and deceleration, and is partially modified so that the landing velocity Vf can be obtained before landing.

When the cage is lowered, when the passenger gives a command, the opening degree command means 42 outputs an excitation signal of the solenoid 45a of the descending control valve 45. Actuator 44 due to cage weight
However, the signal pattern Sd [see FIG. 35 (b)] is such that the opening of the lowering control valve 45 is initially small and gradually increases to increase the amount of oil discharged from the actuator 44. ing. The opening degree of the lowering control valve 45 is kept large so that the actuator 44 contracts at a constant total speed Vjd after a lapse of a predetermined time.

The deceleration limit switch is actuated when the car approaches the deceleration position due to the descent of the cage, and a signal for weakening the exciting force of the solenoid 45a is output from the opening command means 42 so as to gradually reduce the opening of the descending control valve 45. . When reaching the landing speed Vf, a signal for maintaining the opening for a predetermined time is applied to the solenoid 45a, and when the stop limit switch for floor alignment is activated, the signal from the opening command means 42 is stopped.

The signal waveform thus operated is similar to the diagram showing the cage speed, and is substantially equal to the oil amount waveform passing through the ascending control valve 43 and the descending control valve 45.

By the way, when the elevator is started up, the rising control valve that bleeds off the pump flow rate is shifted to the closing operation, and the valve internal pressure is slightly higher than the actuator pressure based on the load acting on the cage (hereinafter referred to as cage pressure). Increase the pressure until In this case, it is necessary to complete the boosting within a predetermined time to start the cage without shock.

The main cause of the start shock is a sudden change in the valve pressure up to the cage pressure immediately before the cage starts, and as the cage pressure increases, that is, as many people get on the cage, the initial bleed-off pressure and the cage pressure increase. The larger the difference from the pressure, the more the starting shock tends to increase.

The countermeasures that have been conventionally adopted in the electric control method described above are to apply a pulse voltage whose width and height have been adjusted immediately after the rising command to temporarily close the bleed-off rising control valve. , The internal pressure of the valve is increased, and the delay in the opening of the valve is used to suppress the sudden pressure change to the cage pressure.

On the other hand, in the hydraulic pilot system, the notch shape of the valve opening of the raising control valve is used, and a shape that reduces by a factor of 1/2 of the valve stroke, for example, is selected so that sudden changes in valve pressure do not occur. And soften the starting shock.

[Problems to be Solved by the Invention]

In any of the elevator valve devices described above, the speed of the cage is determined by the amount of hydraulic oil that passes through the ascending control valve and the descending control valve. If the amount of oil is constantly reproduced, it is possible to raise and lower the cage while maintaining the desired lifting speed and ride comfort, but in reality, the number of passengers in the cage will differ each time, so it will act on the actuator. The pressure applied, that is, the cage pressure, is not always the same.

In the case of the above-mentioned electric control method, it is necessary to adjust the width and height of the pulse voltage at the start of rising for each cage specification.
For example, even if the pulse width and height that are appropriate for a certain loading load of the cage are selected, if the cage pressure changes and it is small, the cage will be momentarily instead of suppressing the starting shock. It will rise a little, and it will be impossible to fully implement measures to mitigate the starting shock.

On the other hand, the hydraulic pilot system cannot fundamentally solve the increasing tendency of the starting shock accompanying the increase of the cage pressure. This is because the position of the opening differs depending on the cage pressure, and it is not possible to keep the degree of area reduction the same. Therefore, if the cage pressure becomes higher, the notch opening area is slightly displaced in advance to a smaller area, and if the valve closing is started from there, the degree of decrease in the area rapidly increases and the starting shock cannot be suppressed.

By the way, in the hydraulic pilot type hydraulic elevator valve device, as described above, for example, a hydraulic pilot type raising control valve for controlling the amount of oil supplied from the hydraulic pump when the cage is raised is adopted, An electromagnetic control valve that applies pilot pressure to it has conventionally been an on / off valve [for example, "Hydraulic pressure and air pressure", Vol. 17, No. 16, 16).
Page].

With such a hydraulic pilot structure, it is almost impossible to perform fine control in response to changes in cage pressure. Therefore, the acceleration / deceleration, the constant (total) speed, and the landing speed differ depending on the cage pressure, which affects the mobility and riding comfort of the cage.

On the other hand, in the hydraulic elevator valve device shown in FIG. 34, which is controlled by an electric waveform signal, the amount of oil supplied to and discharged from the actuator 44 is detected by the flow sensor 46 in the device and converted into a voltage. The differential voltage is further compared with the command voltage signal and the solenoid 43 of the ascending control valve 43 or the descending control valve 45 is further compared.
A predetermined amount of oil is achieved by applying to a and 45a.

However, in such feedback control, there is a problem that initial adjustment of proportional, integral, and derivative gains becomes complicated. In addition, if the adjustment is improper, the operation of the ascending control valve and the ascending control valve is lacking in stability, causing a problem of valve vibration.

In this case, since feedback control is performed to make the supply / discharge amount to the actuator constant, it is not affected by the pressure change as described above, but since the flow rate sensor is built in the elevator valve device, The cost of the device is increased, and the hydraulic elevator valve device becomes extremely complicated.

By the way, in Japanese Utility Model Laid-Open No. 58-41759, a set speed command is output to the main control valve when the cage is raised, and the hydraulic oil from the hydraulic pump is bleed off via the main control valve. A control device for a hydraulic elevator is described.

This involves interposing a fixed throttle and an electromagnetic control valve that operates by receiving a preset control signal in a pilot circuit that branches from an oil passage toward the actuator. And
The pressure on the downstream side of the fixed throttle is controlled by the electromagnetic control valve to act as the pilot pressure of the main control valve, and the downstream side pressure is balanced with the spring force arranged on the other side of the main control valve. Are trying to control.

If the number of passengers in the cage now increases, the pressure in the oil passage increases and the downstream pressure also increases, so the valve opening of the main control valve decreases and the cage speed increases. Conversely, if the number of passengers decreases, the speed of the cage will decrease.

In order to prevent the cage speed from changing with respect to such a change in the load state, it is necessary to control the valve opening degree of the electromagnetic control valve according to the load state. In order to realize that, the amount of oil is detected by a flow meter interposed in the oil passage, compared with the command value, and a correction value is sequentially given to the electromagnetic control valve to adjust the valve opening of the main control valve. .

This is a flow rate feedback control, and as in the above-mentioned example, there are drawbacks that initial adjustment is complicated, a highly sensitive detection function is imposed on the flow meter, and stable operation cannot be expected sufficiently.

The present invention has been made in view of the above problems, and an object thereof is to be applicable to a hydraulic elevator valve device that adopts a hydraulic pilot system, and to avoid the trouble of electric adjustment by adopting an electric open control system that does not require gain adjustment. In addition, even if the pressure acting on the actuator (cage pressure) changes, it is possible to improve the ride comfort of the cage by suppressing the occurrence of a rising start shock due to the increase of the cage pressure. It is an object of the present invention to provide a hydraulic elevator valve device that can obtain a stable linear control characteristic that does not depend on load pressure as an electromagnetic proportional flow rate control system using a fixed throttle downstream.

[Means for Solving the Problems]

The present invention includes a normally open type ascending control valve and a normally closed type ascending control valve, and adjusts the opening of each valve to control the amount of oil from a hydraulic pump or an actuator. It is applied to the hydraulic elevator valve that keeps the speed of the.

As for the feature, referring to FIG. 1, a check valve 14 is interposed in an oil passage 16 connected to an actuator 6 for moving the hydraulic pump 4 and the cage 5 up and down. A bleed-off circuit in which a normally open type rising control valve 2 is arranged is provided branching from the oil passage. An ascending hydraulic pilot circuit that applies a pilot pressure to the pilot chamber 2A of the ascending control valve 2 is provided in parallel with the bleed-off circuit in a continuous manner with the oil passage on the hydraulic pump side. In the ascending hydraulic pilot circuit, an ascending electromagnetic proportional pilot valve 7 having a pressure reducing valve structure whose opening is adjusted in response to a control signal and a secondary solenoid valve which is located downstream of the ascending electromagnetic proportional pilot valve 7 An upstream downstream fixed throttle 8 that regulates the amount of pilot oil according to the pressure and an upstream upstream fixed throttle 9 that generates a differential pressure between the upstream and downstream from the pilot flow generated by the downstream downstream fixed throttle 8 are interposed. To be dressed. And the pilot chamber of the raising control valve 2
The downstream pressure P1 of the upstream upstream fixed throttle 9 is introduced into 2A as a pilot pressure, and the upstream pressure of the upstream upstream fixed throttle 9 is introduced into the bleed-off chamber 2B facing the pilot chamber 2A.
Pp is being introduced.

On the other hand, an exhaust circuit in which a normally closed type descent control valve 3 is arranged is provided branching from an oil passage on the actuator side with the check valve 14 as a boundary. A lowering hydraulic pilot circuit for applying a pilot pressure to the pilot chamber 3A of the lowering control valve 3 is arranged in parallel with the exhaust circuit in a manner connected to the actuator-side oil passage. The descending hydraulic pilot circuit has a reducing electromagnetic proportional pilot valve 10 whose opening is adjusted by receiving a control signal, and a secondary electromagnetic proportional pilot valve 10 located downstream of the secondary electromagnetic proportional pilot valve 10. The downstream fixed throttle 11 for descending that regulates the amount of pilot oil according to the pressure, and the upstream fixed throttle 12 for descending that is located upstream and generates a differential pressure between the pilot flow generated by the downstream fixed throttle 11 for descending before and after. To be dressed. Then, in the pilot chamber 3A of the descending control valve 3, a descending upstream fixed throttle is installed.
The descending side pressure P3 of 12 is introduced as a pilot pressure, and the upstream side pressure P of the descending upstream fixed throttle 12 is introduced into the exhaust chamber 3B facing the pilot chamber 3A. Then, the downstream pressure P3 of the downstream fixed upstream throttle 12 is introduced into the pilot chamber 3A of the lowering control valve 3 as pilot pressure, and the upstream upstream fixed throttle 12 upstream of the downstream upstream fixed throttle 12 is introduced into the exhaust chamber 3B facing the pilot chamber 3A. The side pressure P is introduced, and opening degree commanding means 23 is provided for outputting a solenoid drive signal of an ascending or descending command pattern to each of the electromagnetic proportional pilot valves 7 and 10 as an open loop control signal. Further, pressure detecting means 25 for detecting the pressure Pc of the hydraulic oil acting on the actuator 6 before the cage 5 starts to rise is installed in the actuator oil passage,
In order to suppress the shock generated at the start of the ascent, the above-mentioned opening degree command means 23 raises the cage 5 to such an extent that the cage pressure Pc of the hydraulic oil acting on the actuator 6 before the ascent of the cage 5 is not exceeded. A starting start signal I us for raising the pre-start valve pressure Pv of the control valve 2 from the bleed-off pressure Pb in advance is selected based on the pressure signal from the pressure detection means 25, and the starting start signal I us is selected. A pre-start boost command section 28 (see FIG. 17) that is added to the pre-start solenoid drive command signal when rising is provided.

The feature of the second invention is that, in addition to the above-mentioned configuration, the opening command means 23 has a control valve for raising 2 that is larger than the start signal Ius and does not exceed the cage pressure Pc. A valve internal pressure increase signal I up for raising the pre-start valve internal pressure Pv from the bleed-off pressure Pb in advance is selected based on the pressure signal from the pressure detection means 25, and the valve internal pressure increase signal I up is selected as the start signal. This means that a pre-start preceding excessive boost command unit 31 (see FIG. 29) that is added to the solenoid drive command signal at the time of rising is added before I us.

[Action]

When there is a command to raise the cage 5, the opening degree of the electromagnetic proportional pilot valve 7 for raising of the pressure reducing valve structure is adjusted according to a command pattern which is an open loop control signal from the opening command means 23. As a result, a predetermined pilot pressure P1 is generated in the raising hydraulic pilot circuit of the raising control valve 2, and the opening of the raising control valve 2 is increased by the pressure difference Pp-P1 acting before and after the valve body of the raising control valve 2. Is adjusted.

A part of the total amount of oil introduced from the hydraulic pump 4 to the raising control valve 2 and bleeding off is supplied to the actuator 6, and the cage 5 rises. The opening degree of the raising control valve 2 is adjusted according to a command pattern for driving the solenoid of the raising electromagnetic proportional pilot valve 7.

The case of lowering the cage 5 is almost the same, and the opening degree of the lowering control valve 3 is adjusted based on a command pattern for driving the solenoid of the lowering electromagnetic proportional pilot valve 10 of the pressure reducing valve structure. The amount of oil discharged from the actuator 6 flows into the tank 13 according to the opening degree of the descending control valve 3, and the descending speed according to the command pattern is given to the cage 5.

In the above operation, when the pressure of the hydraulic oil acting on the actuator (cage pressure) increases due to a large number of people riding on the cage 5, etc.
The pressure inside the valve will suddenly change until it reaches the cage pressure on the cage start line.

Therefore, when the cage 5 starts to rise, a start start signal selected based on the pressure signal from the pressure detection means 25.
I us is output from the pre-start boost command unit 28 of the opening command unit 23 so as to be added to the solenoid drive command signal when rising. As a result, even if the cage pressure changes, the rise start shock is suppressed, and the riding comfort at the start of the cage 5 is improved.

In the second invention, the start-up start signal I us is not only output from the pre-start boost command section 28 and added to the solenoid drive command signal, but also larger than the start-up start signal I us, and the pressure detection means 25 The valve internal pressure increase signal I up selected based on the pressure signal of
Output from the pre-start preceding excessive boost command section 31 of the opening degree command means 23. Therefore, even if the cage pressure changes, the rise start shock is strongly suppressed, and the riding comfort at the start of the cage 5 is further improved.

〔The invention's effect〕

According to the present invention, the differential pressure across the upstream fixed throttle is controlled by the ascending electromagnetic proportional pilot valve or the descending electromagnetic proportional pilot valve and its downstream fixed throttle, and the downstream pressure of the upstream fixed throttle upstream and downstream differential pressure is increased. Control valve and lowering control valve into the pilot chamber, upstream pressure is introduced into the oil chamber facing each pilot chamber, and the pressure balance determines the valve opening of the rising and lowering control valves. Will be able to.

The ascending electromagnetic proportional pilot valve and the descending electromagnetic proportional pilot valve are electromagnetic proportional pressure reducing valves with a pressure reducing valve structure whose opening is adjusted by receiving a control signal.The secondary pressure is controlled regardless of the primary pressure, and the downstream fixed throttle valve is used. With, it is possible to control the pilot flow rate according to the command regardless of the primary pressure.

Therefore, even if the number of passengers changes and the load pressure changes, the pressure before and after the upstream fixed throttle does not change, and the differential pressure can be changed only by the command current of the rising electromagnetic proportional pilot valve and the falling electromagnetic proportional pilot valve. Can be decided

Further, all the electromagnetic proportional pilot valves are electromagnetic proportional pressure reducing valves, and the fixed throttles are arranged upstream and downstream thereof, so that the differential pressure characteristic with respect to the command current becomes linear.
In this way, since a stable differential pressure characteristic having good linearity that does not depend on the load pressure can be obtained, the open loop control can be performed only by the signal from the opening degree commanding means. This eliminates the need for gain adjustment required for foot-back control, thus avoiding the troublesome electric adjustment in the initial adjustment work of the apparatus.

Furthermore, even if there is a change in the pressure of the hydraulic oil that acts on the actuator, the occurrence of shock at the start of rising is suppressed,
The riding comfort at the start of the cage is improved.

In the second invention, the shock at the start of rising is further reduced.

〔Example〕

Hereinafter, the present invention, based on the drawings showing the embodiment,
The details will be described. FIG. 1 is a hydraulic circuit diagram of a hydraulic elevator valve device 1 adopting a hydraulic pilot system.

It has a normally open type ascending control valve 2 and a normally closed type ascending control valve 3, and adjusts the opening of each of the valves 2 and 3 to raise and lower the hydraulic pump 4 and the cage 5. The amount of oil from the actuator 6 such as a hydraulic cylinder to be controlled is controlled to adjust the speed of the cage 5 to a command value.

A check valve 14 is interposed in a main oil passage 16 for supplying hydraulic oil from the hydraulic pump 4 to the actuator 6 for moving the cage 5 up and down. The ascending control valve 2 is arranged in a bleed-off circuit that branches from the oil passage on the hydraulic pump side with the check valve 14 as a boundary, and the descending control valve 3 as a boundary with the check valve 14 as a boundary. It is arranged in the exhaust circuit that branches from the oil passage on the actuator side.

In such an elevator valve device, a rising hydraulic pilot circuit that applies pilot pressure to the pilot chamber 2A of the rising control valve 2 is arranged in parallel with the bleed-off circuit and is connected to the oil passage on the hydraulic pump side. Further, a descending hydraulic pilot circuit that applies a pilot pressure to the pilot chamber 3A of the descending control valve 3 is also provided in parallel with the exhaust circuit.

The rising hydraulic pilot circuit is provided with a rising electromagnetic proportional pilot valve 7 having a pressure reducing valve structure, the opening of which is adjusted in response to a control signal, and a downstream fixed throttle 8 for rising. Further, there is provided a rising upstream fixed throttle 9 for generating a pilot pressure P1 by the pilot flow generated in the lifting hydraulic pilot circuit and for causing the pressure to act on the pilot chamber 2A of the rising control valve 2.

On the other hand, the descending hydraulic pilot circuit is provided with a descending electromagnetic proportional pilot valve 10 of a pressure reducing valve structure whose opening is adjusted in response to a control signal and a descending downstream fixed throttle 11. Further, there is provided an upstream fixed throttle 12 for descending, which generates a pilot pressure P3 by a pilot flow generated in the descending hydraulic pilot circuit and acts the pilot pressure P3 on the pilot chamber 3A of the descending control valve 3.

Therefore, when the cage 5 rises, the remaining amount of the hydraulic oil supplied from the hydraulic pump 4 that has been bleed-off to the tank 13 according to the valve opening degree of the raising control valve 2 is the check valves 14 and 15. The hydraulic oil is supplied to the hydraulic cylinder 6 via the above, and the amount of hydraulic oil is adjusted. In addition, check valve
Reference numeral 14 is for preventing the hydraulic oil from the hydraulic cylinder 6 from being introduced into the raising control valve 2 when the cage 5 descends.

The pilot pressure P1 applied to the above-mentioned raising control valve 2 is
It is generated as follows. When the rising electromagnetic proportional pilot valve 7 is opened, the pressure on the secondary side of the reducing electromagnetic proportional pilot valve 7, which is a pressure reducing valve structure, does not depend on the pressure P1 on the primary side, and the secondary pressure depends on the valve opening degree. The pressure P2 is regulated while taking the feedback of. According to the secondary pressure P2, the amount qu of oil passing through the rising downstream fixed throttle 8 is determined. That is,
The amount of oil qu passing through the fixed downstream fixed throttle 8 changes in proportion to the opening degree of the rising electromagnetic proportional pilot valve 7.

The pilot flow passes through the upstream upstream fixed throttle 9 downstream of the filter 17, which is interposed upstream of the hydraulic upstream pilot circuit, and the flow thereof causes a differential pressure before and after the upstream upstream fixed throttle 9. That is, the pressure P1 on the downstream side of the rising upstream fixed throttle 9 becomes lower than the pressure Pp in the oil passage 16 through which the hydraulic oil from the hydraulic pump 4 is supplied to the hydraulic cylinder 6. Since this front-to-back differential pressure Pp-P1 changes in proportion to the opening of the rising electromagnetic proportional pilot valve 7, the opening of the rising control valve 7 is adjusted using this differential pressure.

The pressure P1 on the downstream side of the rising upstream fixed throttle 9 acts on the spring chamber 2A which is a pilot chamber of the rising control valve 2, and the bleed-off chamber 2B facing the spring chamber 2A with the valve body 2a interposed therebetween is not formed. ,
The pressure Pp of the oil passage 16 acts. The spring displaces the valve body 2a of the raising control valve 2 that was in the fully open state, reduces the valve opening, and reduces the amount of oil that is bleed-off to the tank 13 via the bleed-off chamber 2B. Therefore, the amount of oil supplied from the oil passage 16 to the hydraulic cylinder 6 is increased accordingly.

On the other hand, the pilot flow of the descending control valve 3 is generated by the descending electromagnetic proportional pilot valve 10 and its descending downstream fixed throttle 11, and the flow of the descending upstream fixed throttle 12 provided downstream of the filter 18 is generated. A differential pressure P-P3 is generated in the front and rear, and the pressure P3 on the downstream side of the differential pressure P-P3 is the spring chamber 3A which is the pilot chamber of the descending control valve 3.
Acts as a pilot pressure.

The exhaust chamber 3B, which faces the valve body 3a, is supplied with the working oil of the pressure P returned from the hydraulic cylinder 6, and the pilot pressure P3 acting on the spring chamber 3A causes the valve opening degree of the descending control valve 3 to rise. Is adjusted, and the amount of hydraulic oil discharged from the hydraulic cylinder 6 is controlled.

An electromagnetic pilot switching valve 20 that opens upon receiving a downward command for the throttle 19 and the cage 5 is interposed in a circuit that bypasses the check valve 15. The electromagnetic pilot switching valve 20 opens immediately when there is a command to lower the cage 5. As described above, the pilot pressure P3 is generated by the flow of the hydraulic oil from the hydraulic cylinder 6 through them, but the check valve 15 is also opened according to the opening operation of the lowering control valve 3 and is discharged. Most of the hydraulic oil flows from the check valve 15 to the tank 13 via the lowering control valve 3.

By the way, an emergency manual valve 21 for directly draining the hydraulic oil from the hydraulic cylinder 6 and lowering the cage 5 to the bottom in an emergency is provided in a circuit directly connected to the tank 13.

Such a hydraulic elevator valve device is built in the valve casing 22 as shown by the chain double-dashed line in the figure, forming an integral valve mechanism. Therefore, three ports P, T, and C are opened in the valve casing 22, and the respective pipings are connected.

By the way, the solenoid proportional pilot valve 7 for ascent and the solenoid proportional pilot valve 10 for descending are respectively connected to the solenoid 7
Although a and 10a are excited to change their opening, opening instruction means 23 for generating the excitation signal is installed.

This is composed of a microprocessor or the like, and when there is a command to move the cage 5 up and down, it receives a command signal from a separately installed controller 24 that controls the hydraulic elevator valve device,
It outputs an electric signal according to a command pattern described later. Further, it comprises a central processing unit, a fixed storage unit, a writing storage unit, a timer, etc., and the fixed storage unit is provided with commands for acceleration / deceleration as shown by the solid lines in FIGS. 2 (a) and 2 (b). The pattern is stored.

The pattern is a current waveform, and each waveform is preliminarily smoothly shaped so that the portions indicated by arrows Xu, Yu, Zu, Xd, Yd, and Zd in the figure are S-shaped curves. When the solenoid drive command signal is received, the cage 5 is shown in FIG. 3 (a).
And as shown in (b), the desired acceleration state during the ascent and descent, the full-speed state of the speeds Vu, Vd and the deceleration state,
Moreover, it is considered that a good ride comfort can be obtained when moving from acceleration to high speed or deceleration to low speed.

In the above-mentioned valve casing 22, a pressure detecting means 25 for detecting the pressure of the hydraulic oil acting on the hydraulic cylinder 6 is installed in a part of the oil passage of the hydraulic cylinder 6, in the vicinity of the C port in the figure. This is, for example, a well-known pressure sensor, and the pressure of the hydraulic oil acting on the hydraulic cylinder 6 (hereinafter, referred to as cage pressure) has changed due to the number of passengers in the cage 5 changing or the weight of luggage changing. It is for detecting the case.

Based on the pressure signal from the pressure detection means 25, the above-mentioned opening degree command means 23 outputs a solenoid drive signal in which the valve flow rate when the cage is raised is compensated and the volumetric efficiency of the hydraulic pump 4 is compensated. A rising signal correcting unit 26 and a descending signal correcting unit 27 that outputs a solenoid drive signal in which the valve flow rate when the cage is descending are output are provided.

The pressure compensation will be described below. As shown in Fig. 4, without pressure compensation, the solenoid proportional pilot valve for lowering
If the respective solenoid drive currents Id1, Id2, Id3, ... Of 10 are kept constant, the corresponding passing oil amounts Qd1, d2, Qd3, ... Of the lowering control valve 3 increase as the pressure increases.

In order to make the oil amounts Qd1, Qd2, Qd3 ... Constant regardless of the pressure, the exciting currents Id1, Id2, Id3 .. In this case, the exciting current applied to the descending electromagnetic proportional pilot valve 10 is as shown by the one-dot chain line when the pressure is higher than that in the case of the standard pressure as shown by the solid line in FIG. When the pressure is low, the current at each time is increased or decreased as shown by the broken line pattern. In this way, when the exciting current pattern is corrected by the descending signal correcting unit 27 according to the pressure, the same downward movement of the cage 5 is always achieved as shown in FIG. 3 (b).

The above is the control of the amount of oil discharged from the hydraulic cylinder 6 when the cage is lowered when the hydraulic pump 4 does not operate.
When the pressure rises, the hydraulic pump 4 operates, so that its volumetric efficiency also needs to be compensated according to the pressure. Similarly to the above, in the opening operation of the ascending electromagnetic proportional pilot valve 7, the following correction is added to the correction to the same effect as in FIG. 5 due to the change in pressure.

The discharge amount Qp of the hydraulic pump 4 decreases as the pressure increases, as indicated by the solid line in FIG. In order to supply the constant oil amount Qu2 to the hydraulic cylinder 6 as shown by the broken line even if the pressure changes, the bleed-off amount Qu1 in the raising control valve 2 needs to be reduced as the pressure rises. In order to reduce the opening degree of the raising control valve 2, it is necessary to increase the opening degree of the raising electromagnetic proportional pilot valve 7. Therefore, the solenoid exciting current of the raising electromagnetic proportional pilot valve 7 must be increased. I won't.

As a result, the rising signal correction unit 26 is adjusted so as to output a drive current that takes into account the compensation of the valve flow rate characteristic due to the change in pressure and the compensation of the change in volumetric efficiency of the hydraulic pump 4, For the drive currents Iu1, Iu2, Iu3 ··· as shown in the figure, the bleed-off amounts Qu11, Qu12, Qu13 · · of the rising control valve 2
. Is obtained, and even if there is a change in pressure to the hydraulic cylinder 6, a constant supply oil amount Qu21, Qu22, Qu23 ... Is realized.

When the pattern of the exciting current according to the pressure is changed by the rising signal correction unit 26 in this way, the same rising motion of the cage 5 is always achieved as shown in FIG. 3 (a) described later. In addition,
The flow rate characteristic with respect to the pressure of each control valve 2, 3 and the pressure characteristic of the volumetric efficiency of the hydraulic pump 4 are grasped in advance, and the data for correcting the solenoid drive current based on the characteristic is stored in the opening command means 23. It is stored in the rising signal correction unit 26 and the falling signal correction unit 27.

In addition to the pressure compensation described above, the opening degree command means 23,
By using the detected value of the cage pressure in the pressure detecting means 25 described above, the control for avoiding the rising start shock is performed even when the number of passengers in the cage 5 changes or the weight of the luggage changes.

Therefore, the opening command means 23 adds a start start signal I us selected on the basis of the pressure signal from the pressure detection means 25 to the solenoid drive command signal before starting at the time of rising, and the pre-start boost command section. 28 (see FIG. 17) is provided. This is to the extent that the cage pressure Pc of the hydraulic oil acting on the actuator 6 before the cage 5 starts to rise is not exceeded.
Bleed-off pressure is used as the internal pressure Pv of the rising control valve 2 before starting
It functions to raise Pb in advance.

The operation of preventing the start shock by adjusting the pressure in the rising control valve 2 by the start start signal I us will be described in detail below.

When the current waveform in the command pattern for acceleration / deceleration shown by the solid line in FIG. 2 (a) above just before the start is gradually increased as shown by the broken line in FIG. The in-valve pressure Pv of a certain rising control valve 2 rapidly rises from the bleed-off pressure Pb to the cage pressure Pc shown by the alternate long and short dash line as shown by the broken line in FIG.

When the in-valve pressure Pv exceeds the cage pressure Pc, it starts to rise as shown in FIG. 3 (a), but at that time, the cage 5 is accelerated as shown by the broken line in FIG. A shock is generated due to vibration. If a lot of load is applied to the cage 5, the cage pressure Pc becomes higher as shown by the chain double-dashed line in FIG. 9, and the pressure rise sudden change Pc-Pb becomes larger and larger.

The rise of the cage 5 also starts a little later, but the shock generated at that time also increases as the cage pressure Pc increases. This is based on the fact that the pressure rising gradient at the time of starting the cage 5 is large. Therefore, it is necessary to suppress the pressure rising gradient when the cage 5 is started in the process of increasing the valve internal pressure Pv to the cage pressure Pc.

For that purpose, the valve internal pressure Pv at the bleed-off pressure Pb may be increased in the initial stage. In order to realize this, the above-mentioned start-up start signal I us is output from the pre-start-up step-up command unit 28, and it is added to the solenoid drive command signal at the time of rising at the initial stage.

This start start signal I us is selected based on the pressure signal from the pressure detecting means 25, and is not always a constant magnitude. That is, as shown in FIG. 11, pressure detection means
When the detected value of the cage pressure Pc by 25 becomes large, the start start signal I us is also set to a variable value.
In the pre-start boost command unit 28, the start start signal such that the current waveform becomes a thick solid line in FIG. 8 when the cage pressure Pc is low.
I us1, and if the cage pressure Ps is high, the current waveform at that time becomes a thin solid line.
It is considered to be 2.

As a result, the valve pressure Pv of the rising control valve 2 is the cage pressure Pc.
When the cage pressure Pc is high, the pressure is increased as shown by the thick solid line in FIG. In any case, the in-valve pressure Pv is raised to such an extent that it does not exceed the cage pressure Pc before the cage 5 is started, and the pressurization gradient immediately before the start is smaller than that in the case of the broken line described above. That is, the acceleration becomes small as shown by the solid line in FIG. 10 regardless of the cage pressure, and the shock at the time of starting is largely reduced.

The operation sequence with the above configuration will be described below. First, the raising control valve 2 is normally open, and the spring 2b
By this action, the valve body 2a is in a pressed state and the valve is fully open.

When a rising command is issued, the hydraulic pump 4 is activated [see FIG. 12], and commands for operation, high speed rising, and low speed rising are input to the controller 24 [FIG. 13 (a), FIG. 14 (a)]. And FIG. 15 (a)]. Now, the raising control valve 2 is in the fully open state, and the amount of hydraulic oil from the hydraulic pump 4 is all in the tank 13
Has been bleeded off (see Fig. 16).

Cage pressure acting on the hydraulic cylinder 6 by the pressure detecting means 25
Pc is detected and its signal is as shown in the block diagram of FIG.
Along with the command signal for the above-mentioned operation or high speed rising, the controller 24 converts the signal into a digital signal through the interface 29 and inputs the digital signal to the opening degree command means 23.

In the pre-start boost command section 28 of the opening degree command means 23, the start start signal I us is selected based on FIG. 11 corresponding to the pressure signal at that time. It is added to the solenoid drive command signal at the time of rising described below.

As a result, the valve body 2a of the raising control valve 2 in the fully open state moves rapidly in the closing direction, and even if the cage pressure Pc changes, the valve of the raising control valve 2 immediately before the cage 5 starts. When the internal pressure Pv is increased and the cage 5 is started, the increase gradient is small, the rise start shock is suppressed, and the riding comfort at the start of the cage 5 is improved. Of course, if the cage pressure Pc is different, the corresponding start start signal I us is output as described above.

On the other hand, according to the pressure signal of the cage pressure Pc, the command pattern shown in FIG. 2 (a) stored in advance is a pattern of a broken line or an alternate long and short dash line in consideration of the valve characteristic and the volumetric efficiency of the hydraulic pump 4. The signal is corrected by the rising signal correction unit 26 as described above, and is converted into an analog signal. The voltage-current converter 30 having a constant current characteristic outputs a solenoid exciting current.

When the rising electromagnetic proportional pilot valve 7 is opened by the current, the secondary side pressure P2 corresponding to the opening is defined. An amount of oil qu passing through the rising downstream fixed throttle 8 is generated according to the pressure, and a differential pressure is generated before and after the rising upstream fixed throttle 9. When the opening of the ascending electromagnetic proportional pilot valve 7 changes, the differential pressure
Pp-P1 is further increased, and the bleed-off amount of the raising control valve 2 is gradually reduced.

That is, when the solenoid exciting current of the rising electromagnetic proportional pilot valve 7 increases between times t2 and t3 [see FIG. 2 (a)], the pilot flow rate qu passing through the rising downstream fixed throttle 8 increases [ FIG. 18], and the pressure P2 on the upstream side of the ascending downstream fixed throttle 8 also increases [see FIG. 19].

Therefore, the pump pressure Pp [see FIG. 20] before and after the upstream upstream fixed throttle 9 downstream of the filter 17 interposed in the hydraulic hydraulic pilot circuit provided in the oil passage 16 and the electromagnetic proportional pilot valve 7 for upstream Upstream pressure P1 (See Fig. 21)
The differential pressure Pp-P1 with and increases.

Since the pressure P1 acting on the spring chamber 2A is lower than the pressure Pp acting on the bleed-off chamber 2B, the raising control valve 2 operates in the closing direction. As a result, the pressure Pp in the oil passage 16 gradually increases [see FIG. 20], and when the pressure Pc corresponding to the weight of the cage 5 acting on the hydraulic cylinder 6 and the occupant is slightly higher, the check valve 15 Is opened, the supply of hydraulic oil to the hydraulic cylinder 6 is started, and the cage 5 starts to move upward (see FIG. 3 (a)).

Furthermore, an S-shaped command pattern Xu [see FIG. 2 (a)]
Accordingly, when the solenoid drive current increases, the raising control valve 2 operates in the direction of further closing, and the bleed-off flow rate Qu1 of the raising control valve 2 gradually decreases [see FIG. The supply flow rate Qu2 increases [22nd
The cage 5 is smoothly accelerated [see FIG. 3 (a)].

Next, the command pattern becomes a predetermined high-speed current I ut [see FIG. 2 (a)], the hydraulic cylinder 6 extends at high speed, and the cage 5 rises at the speed Vu [see FIG. 3 (a)]. .

When the cage 5 approaches the upper floor, the deceleration limit switch operates, so that the high speed rising signal in the controller 24 is cut off [see FIG. 14 (a)], and only the low speed rising signal remains [Fig. 15 ( a)], the solenoid exciting current of the ascending electromagnetic proportional pilot valve 7 follows an S-shaped pattern Yu [see FIG. 2 (a)], and operates the ascending control valve 2 in the opening direction.

As a result, the flow rate Qu2 supplied to the hydraulic cylinder 6 decreases (see FIG. 22), while the bleed-off flow rate Qu1 of the raising control valve 2 increases (see FIG. 16), and the cage 5 is decelerated. See FIG. 3 (a)].

Next, the command pattern becomes a predetermined low-speed current I ui [see FIG. 2 (a)], and a low speed rise, that is, a running state due to the landing speed Vf [see FIG. 3 (a)]. When the stop limit switch for floor alignment operates, the controller
The low speed rising signal of 24 is also cut off (see FIG. 15 (a)), the command current is reduced in accordance with a predetermined S-shaped command pattern Zu (see FIG. 2 (a)), and the lifting control valve 2 is a hydraulic pump. Bleed off the total discharge amount Qp of 4 (see Fig. 16) and
Stops (see FIG. 3 (a)).

In order to mitigate the shock when the cage 5 stops, the hydraulic pump 4 is stopped after a certain short time elapses from the stop command after the cage 5 completely stops [see FIG. 12]. .

The descending control valve 3 is normally closed, the valve body 3a is being pressed by the action of the spring 3b, and the valve is fully closed. When the command is to lower the cage 5, the hydraulic pump 4 is not driven [see FIG. 12], and the operation, high-speed lowering, and lower-speed lowering signals are input to the controller 24 [FIG. 13 (b), 14]. See FIG. (B) and FIG. 15 (b)].

The solenoid 20a of the electromagnetic pilot switching valve 20 is excited by a signal from the controller 24 [see FIG. 23], the electromagnetic pilot switching valve 20 is opened, and the hydraulic oil from the hydraulic cylinder 6 flows through the throttle 19, The pressure P in the oil passage 16 rises (see FIG. 24).

In this state, the pressure signal from the pressure detecting means 25 is input to the opening degree commanding means 23 via the controller 24, and the drive current gradually increases in accordance with the pressure-corrected command pattern [see FIG. 2 (b)]. , Solenoid proportional pilot valve for lowering 10
The solenoid excitation of is increased, and the pressure P4 on the secondary side is regulated according to its opening [see FIG. 25].

The amount of oil that passes through the descending downstream fixed throttle 11 according to the pressure
qd is generated (see FIG. 26), and a differential pressure is generated before and after the descending upstream fixed throttle 12. When the opening degree of the descending electromagnetic proportional pilot valve 10 changes, the differential pressure P-P3 thereof further increases, and the amount of oil passing through the descending control valve 3 gradually increases.

That is, the solenoid exciting current of the descending electromagnetic proportional pilot valve 10 increases [see FIG. 2 (b)], and the pilot flow rate qd passing through the descending downstream fixed throttle 11 increases [26th
The pressure P4 on the upstream side of the downstream fixed throttle 11 also increases [see FIG. 25].

Therefore, the pressure P (see FIG. 24) of the oil passage 16 before and after the fixed throttle 12 upstream of the lowering of the filter 18 interposed in the hydraulic pilot circuit for descending provided in the oil passage 16 and the electromagnetic proportional pilot valve for lowering. The differential pressure P-P3 from the upstream pressure P3 of 10 (see FIG. 27) increases. Since the pressure P3 acting on the spring chamber 3A is lower than the pressure P acting on the exhaust chamber 3B, the lowering control valve 3 operates in the opening direction.

The check valve 15 is opened in response to the opening operation of the descending control valve 3. The command current is increased according to the S-shape of the command pattern Xd [see FIG. 2 (b)], the control flow rate Qd of the descending control valve 3 is increased [see FIG. 28], and the descent of the cage 5 is accelerated. [See FIG. 3 (b)]. Next, the command pattern becomes a predetermined high-speed current I dt [see FIG. 2 (b)], and the cage 5
Descends at high speed Vd [see FIG. 3 (b)].

When the cage 5 approaches the lower floor, the deceleration limit switch operates, the high-speed descending signal of the controller is cut off (see Fig. 14 (b)), and the current of the descending electromagnetic proportional pilot valve 10 is gradually decreased according to the command pattern Yd. Let [Fig. 2 (b)
Reference], the lowering control valve 3 is operated in the closing direction. Therefore, the control flow rate Qd of the descending control valve 3 decreases [see FIG. 28] and the cage 5 is decelerated [see FIG. 3 (b)].

Next, the command pattern becomes a predetermined low-speed current I di [second
(See FIG. 3B)], and a low speed running state is set [see FIG. 3B]. When the stop limit switch for floor alignment operates, the low-speed falling signal of the controller 24 is cut off (see FIG. 15 (b)), and the command current decreases in the S-shaped stop pattern of the predetermined pattern Zd [FIG. 2]. (See (b)], the lowering control valve 3 is gradually closed from the closing operation.

In order to mitigate the shock when the cage 5 stops, the solenoid drive signal of the electromagnetic pilot switching valve 20 has a certain short time after the stop command after the lowering control valve 3 is completely closed. It is then shut off (see Fig. 23).

FIG. 29 is a block diagram of a hydraulic elevator valve device having a different configuration, in which the opening command means 23 adds the above-mentioned starting start signal I us to the solenoid drive command signal at the time of rising before starting In addition to the boost command unit 28, a pre-start preceding excessive boost command unit 31 [see FIG. 29] is added.

This is larger than the start signal I us and the cage pressure Pc
To the extent that the pressure does not exceed Pv
The in-valve pressure increase signal I up, which is previously raised from the bleed-off pressure Pb, is selected based on the pressure signal from the pressure detecting means 25, and the in-valve pressure increase signal I up is selected as the start signal I us.
It functions so as to be added to the solenoid drive command signal at the time of rising earlier.

The prevention of the starting shock by adjusting the pressure in the rising control valve 2 by the in-valve rising signal I up and the starting start signal I us will be described below.

The above-mentioned start-up signal I us is designed to be added to the solenoid drive command signal at the time of increase at the initial stage, but even if this signal alone does not sufficiently increase the valve pressure Pv. Therefore, it is considered that the valve pressure Pv can be increased by the valve pressure increase signal I up with the intention of increasing it.

The in-valve pressure increase signal I up is selected based on the pressure signal from the pressure detecting means 25 and is not always a constant magnitude. That is, the valve internal pressure increase signal I up is selected to be larger than the starting start signal I us as shown in FIG. 30, and when the detected value of the cage pressure Pc by the pressure detection means 25 becomes large, the valve internal pressure increase signal is increased. It is a variable value that also increases I up.

In the pre-start preceding excessive boost command section 31, if the cage pressure Pc is low, the current waveform is the valve internal pressure increase signal I up1 such that the thick solid line in FIG. 31 is obtained, and if the cage pressure Pc is high, then The current waveform is a valve pressure increase signal I up2 that becomes a thin solid line, which is earlier than the start start signal I us1 or I us2. As a result, the valve pressure Pv of the rising control valve 2 is increased as shown by the thick solid line in FIG. 32 when the cage pressure Pc is low, and as shown by the thin solid line when the cage pressure Pc is high.

In any case, the in-valve pressure Pv is raised to a level that does not exceed the cage pressure Pc before the cage 5 is started, and the pressurizing gradient immediately before the start is made smaller than that in the case of the broken line described above. The acceleration becomes small as shown in Fig. 33 regardless of the cage pressure, and the shock at the time of starting is largely reduced.

In the above description, the opening degree command means 23 is provided with the pre-start boost command section 28 and the pre-start preceding excessive boost command section 31 as well as the rising signal correcting section 26 and the descending signal correcting section 27. The correction units 26 and 27 of may be provided as necessary,
In the present invention, if at least the former command units 28 and 31 are provided, it is possible to suppress or avoid the shock that is generated when the cage starts, which is the intended purpose.

In that case, in the block diagrams in FIGS. 17 and 29, the signal from the pre-start boost command section 28 and / or the pre-start preceding excessive boost command section 31 is directly converted into the voltage-current converter.
It should output to 30.

As can be seen from the above description, the differential electromagnetic pressure Pp-P1 across the rising upstream fixed throttle 9 is adjusted by the control signal to adjust the opening of the electromagnetic proportional pilot valve for rising 7 and the downstream fixed throttle for rising. 8 and controls the downstream pressure P1 by the downstream fixed throttle 8 for raising the pilot chamber 2A of the raising control valve 2
On the other hand, the throttle upstream pressure Pp is applied to the pilot chamber 2A.
Since the bleed-off chamber 2B is opposed to the bleed-off chamber 2B, the valve opening degree of the raising control valve 2 is determined by the equilibrium of the pressure.

The rising electromagnetic proportional pilot valve 7 is an electromagnetic proportional pressure reducing valve. The secondary pressure P2 is controlled regardless of the primary pressure P1 of the rising electromagnetic proportional pilot valve 7, and the rising downstream fixed throttle 8
The pilot flow rate qu defined by is also controlled independently of the pressure P1. Therefore, the number of passengers changes and the oil passage 16
Differential pressure across the upstream fixed upstream throttle 9 even if the pressure Pp changes
Pp-P1 does not change and can be determined only by the command current of the ascending electromagnetic proportional pilot valve 7.

Further, since the fixed throttle 9 is arranged upstream of the rising electromagnetic proportional pilot valve 7 of the pressure reducing valve structure and the fixed throttle 8 is arranged downstream thereof, the upstream fixed throttle 9 for rising with respect to the command current of the electromagnetic proportional pilot valve 7 for rising. The characteristic of the differential pressure across Pp-P1 is linear. In this way, open loop control that can obtain a stable differential pressure Pp-P1 that does not depend on the load pressure is possible, and therefore the troublesome initial adjustment of the device that is necessary for feedback control is eliminated.

Furthermore, even if there is a change in the pressure of the hydraulic oil that acts on the actuator, the occurrence of shock at the start of rising is suppressed,
The riding comfort when starting the cage is further improved. in addition,
The amount of oil supplied to the actuator and the amount of oil passing through the lowering control valve in accordance with the cage pressure can be set to predetermined values, and acceleration / deceleration of the cage and high speed and low speed running can be maintained at desired values.

Of course, since the solenoid drive command signal of the ascending or descending pattern with the S-curve pattern during acceleration / deceleration is output to each of the electromagnetic proportional pilot valves,
The command signal when moving from acceleration or deceleration to constant speed is smooth, and the ride comfort of the cage is improved.

[Brief description of drawings]

FIG. 1 is a circuit diagram of a hydraulic elevator valve device according to the present invention, and FIG.
3 (a) and 3 (b) are solenoid drive signal waveform diagrams of an ascending electromagnetic proportional pilot valve and an ascending electromagnetic proportional pilot valve whose opening is adjusted by receiving a control signal output from the opening command means, FIG. (A) and (b) are the cage up-and-down velocity diagrams,
FIG. 4 is a change diagram of the amount of oil passing through the lowering control valve when a solenoid drive current without pressure compensation is applied to the solenoid proportional pilot valve, and FIG. 5 is a solenoid drive pilot for lowering the pressure compensated solenoid drive current. Fig. 6 is a diagram of the amount of oil passing through the valve in the lowering control valve when applied to the valve. Fig. 6 shows the change in the amount of discharged oil based on the change in the volumetric efficiency of the hydraulic pump due to the pressure of the hydraulic oil acting on the actuator, and the pressure compensation. Fig. 7 shows the amount of oil supplied to the actuator, and Fig. 7 shows the solenoid drive current applied to the rising electromagnetic proportional pilot valve by pressure compensation, the change in the amount of oil bleed-off from the rising control valve in response to it, and the actuator based on the bleed-off amount. Fig. 8 is an enlarged diagram of the solenoid drive signal waveform of the rising electromagnetic proportional pilot valve before and after the cage is started. , FIG. 9 is changed view of the valve in the pressure increase control valve, variation diagram of the acceleration Figure 10 is acting on the cage,
Fig. 11 is a diagram showing the change of the start signal according to the cage pressure.
Fig. 12 shows the operating state of the hydraulic pump, Fig. 13 (a), (b)
Is the operation signal input to the controller, Fig. 14 (a),
(B) is the high-speed lift signal input to the controller, 15th
Figures (a) and (b) are low speed ascent / descent signals input to the controller, Figure 16 is a change state diagram of the bleed-off amount in the ascending control valve, and Figure 17 is corrected by the detection signal from the pressure detecting means. Block diagram for outputting a solenoid drive signal, Fig. 18 is a change state diagram of the pilot control oil amount at the time of ascent, Fig. 19 is a change diagram of the downstream control pressure of the ascending electromagnetic proportional pilot valve, and Fig. 20 is a hydraulic pump downstream Fig. 21 is a change diagram of the pressure in the oil passage, Fig. 21 is a change diagram of the pilot control pressure of the rising control valve, Fig. 22 is a change diagram of the amount of hydraulic oil supplied to the hydraulic cylinder, and Fig. 23 is an electromagnetic pilot switching valve. Fig. 24 is an opening state diagram of Fig. 24, Fig. 24 is a change diagram of pressure in the return oil passage from the hydraulic cylinder, Fig. 25 is a change diagram of downstream control pressure of the electromagnetic proportional pilot valve for lowering, and Fig. 26 is pilot control during lowering. Figure of change state of oil amount, Fig. 27 Fig. 28 is a diagram showing changes in pilot control pressure for the descending control valve, Fig. 28 is a diagram showing changes in the control amount by the descending control valve when descending, and Fig. 29 is a solenoid for ascending that combines the start signal and the signal for increasing the internal pressure of the valve. Block diagram for outputting solenoid drive signal of proportional pilot valve, Fig. 30 is a diagram of change of valve internal pressure increase signal according to cage pressure, and Fig. 31 is increase before and after cage starts when a valve internal pressure increase signal is given. Enlarged view of solenoid drive signal waveform of solenoid proportional pilot valve for use, Fig. 32 shows change of valve internal pressure of rise control valve when valve internal pressure increase signal is given, and Fig. 33 gives valve internal pressure increase signal Case diagram of acceleration change on cage
Fig. 34 is an example of a hydraulic elevator valve device in the prior art by electric feedback control, Fig. 35 (a),
(B) is a speed change diagram of the cage moving up and down. 2 ... Rise control valve, 2A ... Pilot chamber (spring chamber),
2B ... Bleed-off chamber, 3 ... Descent control valve, 3A ... Pilot chamber (spring chamber), 3B ... Exhaust chamber, 4 ...
Hydraulic pump, 5 ... Cage, 6 ... Actuator (hydraulic cylinder), 7 ... Ascending solenoid proportional pilot valve, 8
...... Upstream fixed throttle for rising, 9 …… Upstream fixed throttle for rising,
10 …… Solenoid proportional pilot valve for descending, 11 …… Downstream fixed throttle for descending, 12 …… Upstream fixed throttle for descending, 23 …… Opening command means, 25 …… Pressure detecting means, 28 …… Boosting command before starting Department,
31 …… Preceding excessive pre-startup command section, I us …… Starting signal, I up …… Internal valve pressure increase signal, P1, P3 …… Pilot pressure, Pc …… Pressure of hydraulic oil acting on actuator (cage pressure ).

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-60-148878 (JP, A) Actual development: S58-41759 (JP, U)

Claims (2)

[Claims] 1. A normal open type ascending control valve and a normally closed type ascending control valve are provided, and the opening of each valve is adjusted to control the amount of oil from a hydraulic pump or actuator, respectively. In a hydraulic elevator valve that keeps the speed of a cage at a command value, a check valve is provided in an oil passage connected to the hydraulic pump and an actuator that moves the cage up and down, and an oil passage on the hydraulic pump side with the check valve as a boundary Is provided with a bleed-off circuit in which the normally open type rising control valve is arranged, and the rising hydraulic pilot circuit that applies pilot pressure to the pilot chamber of the rising control valve is connected to the oil on the hydraulic pump side. Of the pressure reducing valve structure, which is arranged in parallel with the bleed-off circuit in parallel with the road, and whose opening is adjusted by receiving a control signal in the ascending hydraulic pilot circuit. An ascending electromagnetic proportional pilot valve, a downstream fixed throttle for ascending which regulates the amount of pilot oil according to the secondary pressure generated by the ascending electromagnetic proportional pilot valve, and an ascending upstream upstream throttle valve. A fixed upstream upstream restrictor for generating a differential pressure between the pilot flow generated by the downstream fixed upstream throttle and the upstream upstream fixed restrictor is installed in the pilot chamber of the upstream control valve. The upstream side pressure of the upstream fixed upstream throttle is introduced into the bleed-off chamber facing the pilot chamber, and the pressure is branched from the oil passage on the actuator side with the check valve as a boundary. And an exhaust circuit in which the normally closed type lowering control valve is arranged is provided, and a pilot pressure is applied to the pilot chamber of the lowering control valve. Hydraulic pilot circuit is arranged in parallel with the exhaust circuit in series with the hydraulic passage on the actuator side, and the hydraulic pilot circuit for lowering has a reducing electromagnetic proportional pilot of a pressure reducing valve structure for adjusting the opening in response to a control signal. A valve, a downstream fixed throttle for descending that regulates the amount of pilot oil according to the secondary pressure generated by the electromagnetic proportional pilot valve for downstream, and a downstream fixed throttle for downstream that is upstream. A downstream upstream fixed throttle that generates a differential pressure between the generated pilot flow and the downstream is interposed, and the downstream pressure of the downstream upstream fixed throttle is introduced as a pilot pressure into the pilot chamber of the lower control valve. The upstream pressure of the descending upstream fixed throttle is introduced into the exhaust chamber facing the pilot chamber, so that the rising or falling command pattern Renoid drive signal,
An opening command means for outputting to each of the electromagnetic proportional pilot valves as an open loop control signal is provided, and a pressure detection means for detecting the pressure of the hydraulic oil acting on the actuator before the cage starts to rise is provided in the actuator oil passage. The opening commanding means is installed so as to suppress the shock generated at the start of the ascent so that the cage pressure of the hydraulic oil acting on the actuator before the cage starts ascending does not exceed the cage pressure. A start signal for pre-starting the internal pressure of the control valve from the bleed-off pressure is selected based on the pressure signal from the pressure detecting means, and the solenoid drive before starting when the start signal is increased. A hydraulic elevator valve device comprising a pre-starting boost command unit for adding to a command signal. 2. A normal open type ascending control valve and a normally closed type ascending control valve are provided, and the opening of each valve is adjusted to control the amount of oil from a hydraulic pump or actuator, respectively. In a hydraulic elevator valve that keeps the speed of a cage at a command value, a check valve is provided in an oil passage connected to the hydraulic pump and an actuator that moves the cage up and down, and an oil passage on the hydraulic pump side with the check valve as a boundary Is provided with a bleed-off circuit in which the normally open type rising control valve is arranged, and the rising hydraulic pilot circuit that applies pilot pressure to the pilot chamber of the rising control valve is connected to the oil on the hydraulic pump side. Of the pressure reducing valve structure, which is arranged in parallel with the bleed-off circuit in parallel with the road, and whose opening is adjusted by receiving a control signal in the ascending hydraulic pilot circuit. An ascending electromagnetic proportional pilot valve, a downstream fixed throttle for ascending which regulates the amount of pilot oil according to the secondary pressure generated by the ascending electromagnetic proportional pilot valve, and an ascending upstream upstream throttle valve. A fixed upstream upstream restrictor for generating a differential pressure between the pilot flow generated by the downstream fixed upstream throttle and the upstream upstream fixed restrictor is installed in the pilot chamber of the upstream control valve. The upstream side pressure of the upstream fixed upstream throttle is introduced into the bleed-off chamber facing the pilot chamber, and the pressure is branched from the oil passage on the actuator side with the check valve as a boundary. And an exhaust circuit in which the normally closed type lowering control valve is arranged is provided, and a pilot pressure is applied to the pilot chamber of the lowering control valve. Hydraulic pilot circuit is arranged in parallel with the exhaust circuit in series with the hydraulic passage on the actuator side, and the hydraulic pilot circuit for lowering has a reducing electromagnetic proportional pilot of a pressure reducing valve structure for adjusting the opening in response to a control signal. A valve, a downstream fixed throttle for descending that regulates the amount of pilot oil according to the secondary pressure generated by the electromagnetic proportional pilot valve for downstream, and a downstream fixed throttle for downstream that is upstream. A downstream upstream fixed throttle that generates a differential pressure between the generated pilot flow and the downstream is interposed, and the downstream pressure of the downstream upstream fixed throttle is introduced as a pilot pressure into the pilot chamber of the lower control valve. The upstream pressure of the descending upstream fixed throttle is introduced into the exhaust chamber facing the pilot chamber, so that the rising or falling command pattern Renoid drive signal,
An opening command means for outputting to each of the electromagnetic proportional pilot valves as an open loop control signal is provided, and a pressure detection means for detecting the pressure of the hydraulic oil acting on the actuator before the cage starts to rise is provided in the actuator oil passage. The opening commanding means is installed so as to suppress the shock generated at the start of the ascent so that the cage pressure of the working oil acting on the actuator before the cage starts ascending does not exceed the cage pressure. A start signal for pre-starting the internal pressure of the control valve from the bleed-off pressure is selected based on the pressure signal from the pressure detecting means, and the solenoid drive before starting when the start signal is increased. Pre-start boost command section that is added to the command signal, and the pre-start valve internal pressure of the rising control valve that is larger than the above-mentioned start start signal and does not exceed the cage pressure. A valve internal pressure increase signal for preliminarily raising the force from the bleed-off pressure is selected based on the pressure signal from the pressure detection means, and the solenoid drive when the valve internal pressure increase signal is increased before the start start signal is selected. A hydraulic elevator valve device, comprising: a pre-start preceding excessive boost command unit that is added to the command signal.