JPH0192183A - Hydraulic elevator valve gear - Google Patents

Abstract

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

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a hydraulic elevator valve device, and more specifically, it is equipped with an ascending control valve and a descending control valve, and controls the amount of oil from a hydraulic pump or an actuator. The present invention relates to a hydraulic elevator valve device that maintains the car speed at a command value.

[Conventional technology]

As one type of elevator drive device for raising and lowering an elevator car, a hydraulic cylinder is often used when the distance of raising and lowering the car is short. There is an indirect type in which a fixed pulley is installed above the elevator space of the cage and a rope is hung on it to increase the amount of expansion and contraction of the plunger to raise and lower the cage. In any case, by operating an actuator such as a hydraulic cylinder and adjusting the operating speed of the actuator, the elevator valve is designed so that acceleration, constant speed (full speed), and deceleration operation when raising and lowering the cage can be obtained. The amount of hydraulic oil supplied and discharged is controlled by

In order to control the oil supply and discharge amount of an actuator that directly raises and lowers the cage, a hydraulic pilot system is used for the ascending control valve and descending control valve of the elevator valve device;
Electric control methods may be applied. These are equipped with a normally open ascending control valve and a normally closed descending control valve to control the amount of oil from the hydraulic pump and actuator to maintain the cage speed at the command value. .

In the former hydraulic biloft system, the valve bodies of the ascending control valve and the descending control valve are displaced by pilot pressure. Each hydraulic pilot circuit has an electromagnetic control valve, and by turning the electromagnetic control valve on and off based on elevator lift commands, it is possible to adjust the amount of oil supplied to the actuator when ascending or to control the amount of oil supplied to the actuator when descending. The amount of oil discharged from the tank is adjusted.

On the other hand, in the latter electric control method, both the ascending control valve and the descending control valve are electromagnetic control valves, and a pre-stored current pattern is given to the solenoid to change the degree of excitation, and each control valve directly applies oil. I'm trying to adjust the amount. This latter type of hydraulic elevator valve is described in "Elevator World", Vol. 21, No. 84, page 25, published by the Japan Elevator Association.

Of the above two types of hydraulic elevator valves, taking the latter as an example,
The control will be explained. When raising the cage, when the passenger gives the command, the hydraulic pump 31 shown in FIG.
At the same time, the opening command means 32, such as a microcomputer, outputs a signal that excites the solenoid 33a of the electromagnetic proportional valve 33, which is a rising control valve. The signal has a pattern that starts small and gradually increases to increase the amount supplied to the actuator 34.

The opening degree of the ascending control valve 33 is kept small so that the actuator 34 extends at a constant full speed after a predetermined period of time has elapsed. When the cage approaches the deceleration position as it rises, the deceleration limit switch is activated, and the opening command means 32 sends the rising I
I) A signal for weakening the excitation force of the solenoid 33a is output based on the memorized pattern in order to gradually increase the opening degree of the control valve 33. When the landing speed reaches about 1/8 to 1/10 of the full speed, a signal is sent to maintain the opening for a predetermined period of time.
The voltage is applied to the solenoid 33a. When the stop limit switch for floor alignment is activated, the signal from the opening command means 32 is stopped. Such a signal pattern, for example, as shown in FIG. 29(a), is a roughly trapezoidal current waveform Su that realizes acceleration, constant speed Vju, and deceleration, and a landing speed Vf is obtained before landing. As such, it has been partially modified.

When the car is lowered, when there is a command from the passenger, the solenoid 35 of the lowering control valve 35 is activated by the opening command means 32.
The excitation signal of a is output. The actuator 34 contracts due to the cage's own weight, but the signal pattern Sd (see FIG. 29(b)) shows that the opening of the lowering control valve 35 is initially small and then gradually increased to increase the amount of oil discharged from the actuator 34. The opening degree of the lowering control valve 35 is kept large so that the actuator 34 contracts at a constant full speed Vjd after a predetermined time has elapsed.The lowering control valve 35 approaches the deceleration position by lowering the cage. The deceleration limit switch is activated, and the opening command means 32 outputs a signal to gradually reduce the opening of the descending control valve 35, weakening the excitation force of the solenoid 35a.When the landing speed Vf is reached, When a signal to maintain the opening degree for a predetermined period of time is applied to the solenoid 35a and a stop limit switch for floor alignment is activated, the signal from the opening degree command means 32 is stopped.

The signal waveform operated in this manner is similar to the diagram showing the car speed, and the rising control valve 33 and the descending control valve 35
It is roughly equal to the oil flow waveform passing through.

[Problem that the invention seeks to solve]

In any of the elevator valve devices described above, the speed of the car is determined by the amount of hydraulic fluid passing through the ascending control valve and the descending control valve. If the amount of oil is always reproduced, the cage can be raised and lowered while maintaining the desired lifting speed and riding comfort.However, in reality, the number of occupants in the cage varies each time, so the actuator The hydraulic pressure used is not always the same. If the oil pressure is different, the valve flow rate depending on the valve opening degree of the ascending control valve and descending control valve will also be different. If the excitation current of the control valve is kept the same even when the pressure changes, that is, if the valve opening is kept the same, the flow rate passing through the valve will increase as the pressure increases. As a result, even if the valve is opened to a desired degree, if the pressure is changing, the amount of oil supplied to and discharged from the actuator will not be as desired, and the speed of elevation of the cage will change.

The influence of such pressure changes not only changes the amount of oil passing through each control valve, but also affects the volumetric efficiency of the hydraulic pump that supplies hydraulic oil to the actuator. In other words, as the pressure increases, the pump discharge rate decreases, so
When raising the cage, the opening degree of the control valve must be adjusted in anticipation of changes in the pump discharge amount.

As mentioned above, in a hydraulic pilot type hydraulic elevator valve system, for example, a hydraulic biloft 2 lift control valve is used to control the amount of oil supplied from a hydraulic pump when the car is raised. The electromagnetic control valve that applies pressure has traditionally been an on-off valve (see, for example, "Hydraulics and Pneumatics", Vol. 17, No. 3, page 16). With such a hydraulic pilot structure, it is nearly impossible to perform fine control in response to changes in the pressure acting on the actuator. Therefore, the acceleration/deceleration, constant speed (full speed) speed, and landing speed vary depending on the pressure of the hydraulic oil acting on the actuator, which poses a problem of affecting the mobility and riding comfort of the cage.

On the other hand, in the hydraulic elevator valve device shown in FIG. 28, which is controlled by electrical waveform signals, the amount of oil supplied to and discharged from the actuator 34 is detected by a flow sensor 36 within the device, and this is converted into voltage. A predetermined oil amount is achieved by comparing the differential voltage with the command voltage signal and further applying the differential voltage to the solenoids 33a and 35a of the ascending control valve 33 or the descending control valve 35. However, such feedback control has a problem in that initial adjustment of proportional, integral, and differential gains is complicated. In addition, if there is a defect in the adjustment, the operation of the ascending control valve and the descending control valve will become unstable, resulting in problems such as valve vibration.

In this case, feedback control is performed to keep the supply and discharge amount to the actuator constant, so it is not affected by pressure changes as described above, but since the flow sensor is built into the elevator valve device, This increases the cost of the equipment and also makes the hydraulic elevator valve system extremely complex.

The present invention was made in view of the above problems, and its purpose is to be applicable to a hydraulic elevator valve device that employs a hydraulic pilot system, and to avoid the troublesome electrical adjustment by adopting an electric oven control system that does not require gain adjustment. Even if the pressure acting on the actuator changes, the amount of oil passing through each control valve is approximately the desired value, ensuring cage acceleration, deceleration, high-speed running speed, and landing speed. It is an object of the present invention to provide a hydraulic elevator valve device.

[Means for solving problems]

The present invention includes a normally open ascending control valve 2 and a normally closed descending control valve 3 shown in FIG. It is applied to a hydraulic elevator valve that controls the amount of oil from the cage 5 and maintains the speed of the cage 5 at a command value. Its features will be explained with reference to the symbols attached to the drawings. The hydraulic pilot circuit of the ascending control valve 2 is provided with an ascending electromagnetic proportional pilot valve 7 and a downstream fixed throttle 8, and a pilot pressure P1 is generated by the flow generated in the hydraulic pilot circuit, and the pressure is controlled for ascending. A fixed throttle 9 is interposed that acts on the pilot chamber 2A of the valve 2. On the other hand, a descending electromagnetic proportional pilot valve 10 is connected to the hydraulic pilot circuit of the descending control valve 3.
and a downstream fixed throttle 11 are provided, and a pilot pressure P3 is generated by the flow generated in the hydraulic pilot circuit, and the pressure is transferred to the biloft chamber 3A of the lowering control valve 3.
A fixed diaphragm 12 is interposed to act on the diaphragm. and,
Solenoid drive signal of up or down command pattern,
Opening command means 24 is provided for outputting to each electromagnetic proportional pilot valve 7.10. In addition, a notch 26 shown in FIGS. 4 and 5 is formed in the valve body 18 of the ascending control valve 2 and descending control valve 3, and the notch 26 has a streamline angle θ of the hydraulic fluid. It has a decreasing slope or arc shape.

[For production]

When there is a command to raise the cage 5, the opening degree of the raising electromagnetic proportional pilot valve 7 is adjusted according to a command pattern from the opening command means 24. As a result, the control valve 2 for raising
A predetermined pilot pressure Pl is generated in the hydraulic pilot circuit, and the opening degree of the ascending control valve 2 is adjusted by the pressure difference Pp - PL acting before and after the valve body 18 of the ascending control valve 2.

A part of the total amount of oil introduced from the hydraulic pump 4 into the lifting control valve 2 and bled off is supplied to the actuator 6, and the cage 5 is raised. The opening degree of the ascending control valve 2 is adjusted according to a command pattern for driving the solenoid of the ascending electromagnetic proportional pilot valve 7, and the cage 5 rises according to the amount of supply to the actuator 6. At this time, it is an open-loop control system in which only signals based on command patterns are input, and there is no cumbersome feedback control for gain adjustment.

The case of lowering the cage 5 is substantially the same, and the opening degree of the lowering control valve 3 is adjusted based on the command pattern for driving the solenoid of the lowering electromagnetic proportional pilot valve 10.

The amount of oil discharged from the actuator 6 flows into the tank 13 according to the opening degree of the lowering control valve 3, and the lowering speed according to the command pattern is given to the cage 5.

In the above operation, if the pressure of the hydraulic oil acting on the actuator changes, even if the opening degrees of each control valve 2 and 3 are made as instructed, the amount of oil supplied and discharged from the actuator and the amount of oil discharged from the hydraulic pump will change. This will result in a change in quantity. When the cage 5 rises, the hydraulic oil bleeds off through the notch 26 formed in the valve body 18 of the rising control valve 2. The oil streamline angle θ becomes smaller. In the lift control valve 2, the valve body 18 moves from the fully open state to the closed direction, functioning to increase the amount of oil supplied to the actuator 6, but the pressure P of the inflowing hydraulic oil and the bleed The larger the difference in the pressure of the hydraulic oil that is turned off, the more the valve body 18 is moved in the direction of closing due to the fluid reaction force of the hydraulic oil. Therefore, when it is necessary to increase the pressure acting on the actuator 6 due to many people on board, etc., the lift control valve 2 has a bleed-off amount determined by the shape of the notch 26, and the amount of bleed-off to the actuator 6 is determined by the shape of the notch 26. The supply amount is set to a desired value regardless of the pressure of the hydraulic oil from the hydraulic pump 4. Such operations are performed in the same way when running at full speed or at the landing speed.

On the other hand, when the cage 5 descends, the opening degree of the descending control valve 3 is increased, but similarly to the above, the valve body 18 moves slightly in the direction of closing due to the fluid reaction force. As a result, even if the amount of oil flowing from the descending control valve 3 to the tank 13 tends to increase due to the high pressure of the actuator 6, the amount of oil is limited, regardless of the pressure of the hydraulic oil acting on the actuator 6. It is assumed to be a desired value.

〔Effect of the invention〕

The present invention provides the hydraulic pilot circuit of the ascending control valve with an ascending electromagnetic proportional pilot valve and a downstream fixed throttle, and interposes a fixed throttle that generates pilot pressure by the pilot flow. The pilot circuit is provided with a descending electromagnetic proportional pilot valve and a downstream fixed throttle, and a fixed throttle is interposed to generate pilot pressure by the pilot flow. Since the proportional pilot valve is subjected to oven loop control, there is no need for gain adjustment that is required in the case of feedback control, and the troublesome electrical adjustment in the initial adjustment work of the device is avoided. Furthermore, even if there is a change in the pressure of the hydraulic oil acting on the actuator, the amount of oil supplied to the actuator during ascending and the amount of hydraulic oil passing through the descending control valve during descending can be set to desired values. Therefore, even with the hydraulic pilot type elevator valve, the car can always be given a desired acceleration/deceleration speed and can be made to travel at high and low speeds.

〔Example〕

Below, the present invention will be explained based on the drawings showing the embodiments thereof.
Explain in detail. FIG. 1 is a hydraulic circuit diagram of a hydraulic elevator valve device 1 that employs a hydraulic biloft system.

This is equipped with a normally open type lifting control valve 2 and a normally closed type lowering control valve 3, and adjusts the opening degree of each valve 2.3 to move the hydraulic pump 4 and cage 5 up and down. The speed of the cage 5 is adjusted to a specified value by controlling the amount of oil from an actuator 6 such as a hydraulic cylinder. Such an elevator valve device includes
The hydraulic pilot circuit of the ascending control valve 2 is provided with an ascending electromagnetic proportional pilot valve 7 having a pressure reducing valve structure and a downstream fixed throttle 8. Further, a fixed throttle 9 is provided which generates a pilot pressure P1 by the pilot flow generated in the hydraulic pilot circuit and causes the pressure to act on the pilot chamber 2A of the rising control valve 2.

On the other hand, in the hydraulic pilot circuit of the descending control valve 3, a descending electromagnetic proportional pilot valve IO having a pressure reducing valve structure and a downstream fixed throttle 11 are arranged. Furthermore, a pilot pressure P3 is generated by the pilot flow generated in the hydraulic pilot circuit, and the pressure is applied to the pilot chamber 3 of the lowering control valve 3.
A fixed throttle 12 that acts on A is interposed.

Therefore, when the cage 5 rises, the remaining amount of the hydraulic oil supplied from the hydraulic pump 4 is drained off to the tank 13 according to the opening degree of the lift control valve 2, and the remaining amount is passed through the check valve 14.15. The hydraulic oil is supplied to the hydraulic cylinder 6, and the amount of hydraulic oil therein is adjusted. The check valve 14 is provided to prevent hydraulic oil from the hydraulic cylinder 6 from being introduced into the lifting control valve 2 when the cage 5 is lowered.

The pilot pressure P1 that is applied to the rise control valve 2 is generated as follows. When the ascending electromagnetic proportional pilot valve 7 opens, the pressure on the secondary side of the ascending electromagnetic proportional pilot valve 7, which has a pressure reducing valve structure, changes to the secondary according to the valve opening degree, regardless of the pressure P1 on the negative side. The pressure P2 is defined while taking pressure feedback. The amount of oil 1itqu passing through the downstream fixed throttle 8 is determined according to the secondary pressure P2. That is, the amount of oil qu passing through the downstream fixed throttle 8 changes in proportion to the opening degree of the ascending electromagnetic proportional pilot valve 7. The pilot flow passes through the fixed throttle 9 on the downstream side of the filter 17 which is interposed in a hydraulic pilot circuit installed in the oil passage 16, and a pressure difference is generated before and after the fixed throttle 9 due to the flow. That is, the pressure P1 on the downstream side of the fixed throttle 9
is 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 differential pressure pp-pt changes in proportion to the opening degree of the ascending electromagnetic proportional pilot valve 7, the opening degree of the ascending control valve 7 is adjusted using this differential pressure.

That is, the pressure P1 on the downstream side of the fixed throttle 9 acts on the spring chamber 2A, which is the pilot chamber of the lift control valve 2, and the flow chamber 2B, which faces the spring chamber 2A with the valve body 18u in between, is filled with oil. The pressure pp in line 16 acts. The valve body 18u of the rising control valve 2, which was in the fully open state, is moved by the spring 2b,
The valve opening becomes smaller, and the amount of oil bled off to the tank 13 via the circulation chamber 2B is reduced. Therefore, the amount of oil supplied from the oil passage 16 to the hydraulic cylinder 6 is increased accordingly.

On the other hand, a pilot flow of the descending control valve 3 is generated by the descending electromagnetic proportional pilot valve 10 and its downstream fixed throttle 11, and the flow causes a pressure difference P before and after the fixed throttle 12 disposed downstream of the filter 19. −P3 occurs, and the pressure P on the downstream side
3 is a spring chamber 3A which is a pilot chamber of the descending control valve 3;
, it acts as a pilot pressure P3. The hydraulic oil at the pressure P returned from the hydraulic cylinder 6 is supplied to the circulation chamber 3B which faces the valve body 18d, and the valve opening of the lowering control valve 3 is controlled by the pilot pressure P3 acting on the spring chamber 3A. is adjusted, and the amount of hydraulic oil discharged from the hydraulic cylinder 6 is controlled. In addition, check valve 1
An electromagnetic pilot switching valve 21 that opens in response to a command to lower the throttle 20 and the cage 5 is interposed in a circuit that bypasses the cage 5.

The electromagnetic pilot switching valve 21 opens immediately upon receiving a command to lower the cage 5. As mentioned above, the pilot pressure P3 is generated by the flow of hydraulic oil from the hydraulic cylinder 6 through these valves. However, in response to the opening operation of the descending control valve 3, the check valve 15 also opens, and most of the discharged hydraulic oil flows from the check valve 15 to the tank 13 via the descending control valve 3. An emergency manual valve 22 is provided in a circuit directly connected to the tank 13 for directly draining the hydraulic oil and lowering the cage 5 to the lowest position in an emergency. It is built into the valve casing 23 as shown by the dashed line to form an integrated valve mechanism.Thus, three ports P, T, and C are opened in the valve casing 23, and each piping is connected to the valve casing 23. There is.

By the way, the above-mentioned solenoid proportional pilot valve 7 for ascending and proportional electromagnetic pilot valve 10 for descending have their respective solenoids 7a and loa energized to change their opening degree, but the excitation signal is generated. Opening command means 24
is installed.

This is composed of a microprocessor, etc., and when there is a command to raise or lower the cage 5, it receives a command signal from a separately installed controller 25 that controls the hydraulic elevator valve device, and outputs an electric signal according to the command pattern described later. It is something to do. This consists of a central processing unit, a fixed storage section, a write storage section, a timer, etc. The fixed storage section stores command patterns for acceleration and deceleration as shown by solid lines in FIGS. 2(a) and 2(b). The pattern is a current waveform, and each waveform has been smoothly shaped in advance so that the portions indicated by arrows Xu, Yu, Zu, Xd, Yd, and Zd in the figure form S-shaped curves. When the solenoid drive command signal is received, the cage 5 attains the desired acceleration, full speed Vu, Vd, and deceleration state when ascending and descending, as shown in FIGS. 3(a) and 3(b). Consideration has been given to ensuring a good ride comfort when driving at high speeds or when transitioning from deceleration to low speed driving.

Valve body 18u of the above-mentioned ascending control valve 2 and descending control valve 3
, 18d are formed with notches '15u, 26d as shown in FIGS. It is designed so that adjustments can be made automatically when the pressure of the hydraulic oil acting on the system changes. By the way, to describe the structure of a valve device commonly used in a normal ascending control valve 2 and descending control valve 3, using the descending control valve 3 shown in FIG. A pressure drop occurs when the fluid flows out into the groove 27, and at this time, a fluid reaction force Fh is generated that generates a force in the closing direction on the valve body 18. This is expressed as Fh=kQvcosθ: constant Q: flow rate V: flow velocity θ: streamline angle, and while the opening area A becomes smaller due to the movement of the valve body 18,
Since there is an increase in p-pt, the fluid reaction force therefore also does not change significantly.

On the other hand, the plurality of oil grooves 2B formed in the valve body 18 have a constant depth as shown in FIG. It reduces the power. In this way, the influence of the fluid reaction force on the valve body 18 is normally minimized, but in the present invention, as p-pt increases, the resulting fluid reaction force becomes even larger. This is taken into consideration. For this purpose, the above-mentioned notch 2
6 is connected to a plurality of oil grooves 28 formed around the circumference of the valve body 18 as shown in FIGS. 4 and 5, and has an inclined or arcuate shape that reduces the streamline angle θ of the hydraulic oil. There is. Note that if the constant k of the springs 2b and 3b is selected based on experimental data, a desired compensation function for pressure and flow rate can be achieved.

The pressure compensation will be briefly explained below. As shown in FIG. 7 without pressure compensation, if each solenoid drive current Id of the descending electromagnetic proportional pilot valve 10 is kept constant, the corresponding oil amount Qd passing through each descending control valve 3 is as follows. As the pressure increases, it increases as shown by the solid line. This oil amount Q
In order to make d constant as shown by the broken line regardless of pressure,
The valve opening degree may be reduced as the pressure acting on the hydraulic cylinder 6 increases. According to the oil groove 28d provided with the above-mentioned notch 26d, the degree of opening of the valve body 18d is suppressed by the large fluid reaction force, and the amount of hydraulic oil that is about to flow into the tank 13 is restricted.

When the pressure is compensated in this way, 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.
Since the hydraulic pump 4 operates when the pressure rises, its volumetric efficiency also needs to be compensated according to the pressure. Similarly to the opening operation of the descending electromagnetic proportional pilot valve 10, the opening operation of the ascending electromagnetic proportional pilot valve 7 is independent of pressure changes (although The valve body 18 moves due to the fluid reaction force generated by the notch 26, and moves slightly in the closing direction based on the above-mentioned principle, thereby compensating pressure and volumetric efficiency.

The operation sequence with the above configuration will be explained next. First, the lift control valve 2 is normally open, and the spring 2
Due to the action of b, the valve body 1.8u is pushed to the right as shown in FIG. Circumferential groove 2
It is bled off to tank 13 via 7u. When there is a command to ascend, the hydraulic pump 4 is started [see Figure 9].
, commands for operation, high-speed ascent, and low-speed ascent are input to the controller 25 (see FIGS. 10(a), 11(a), and 12(a)). In the opening command means 24, when the ascending electromagnetic proportional pilot valve 7 opens with a current based on the command pattern shown in FIG. stipulated. Depending on the pressure, an amount of oil qu passing through the downstream fixed throttle 8 is generated, and a pressure difference is generated before and after the fixed throttle 9. When the opening degree of the ascending electromagnetic proportional viroft valve 7 changes, the differential pressure pp-Pl further increases, and the valve body 18u of the ascending control valve 2
As shown in the figure, move to the left and bleed off amount Qul.
is gradually reduced (see Figure 13). That is, when the solenoid excitation current of the ascending electromagnetic proportional pilot valve 7 increases between times t2 and t3 [see FIG. 2 (a)], and the pilot flow rate qu passing through the downstream fixed throttle 8 increases [14th (see figure), and the pressure P2 on the upstream side of the downstream fixed throttle 8 also increases [see figure 15]. Therefore, the pump pressure P before and after the fixed throttle 9 downstream of the filter 17 interposed in the hydraulic pilot circuit installed in the oil passage 16
The differential pressure Pp between the upstream pressure Pi (see Fig. 17) of the ascending electromagnetic proportional pilot valve 7 (see Fig. 16)
-PL increases. Since the pressure P1 acting on the spring chamber 2A is smaller than the pressure pp acting on the circulation chamber 2B, the rising control valve 2 operates in the direction of closing. As a result, oil path 1
The pressure pp in the hydraulic cylinder 6 gradually increases [see Fig. 16], and when it becomes slightly higher than the pressure Pc corresponding to the weight of the cage 5 and the passenger acting on the hydraulic cylinder 6, the check valve 15 opens and the hydraulic cylinder Supply of hydraulic oil to cage 6 is started, and cage 5 begins to rise [see FIG. 3(a)]. Furthermore, when the solenoid drive current increases according to the S-shaped command pattern Xu (see Fig. 2 (a)), the ascending control valve 2 operates in the direction of closing further, and the bleed-off flow rate of the ascending control valve 2 increases. While Qul gradually decreases [first
3], the supply flow rate Qu2 to the hydraulic cylinder 6 increases [see FIG. 18], and the cage 5 is smoothly applied.
See Figure 3(a)]. Next, the command pattern becomes a predetermined high-speed current of 1 ut (see Fig. 2 (a)), and when the valve IJ3u closes the flow path of the hydraulic oil that bleeds off as shown in Fig. 19, the hydraulic cylinder 6 moves at high speed. Extend cage 5
rises at high speed Vu [see Figure 3(a)].

When the cage 5 approaches the upper floor, the deceleration limit switch is activated, so the high-speed ascent signal in the controller 25 is cut off (see Figure 11 (a)), and only the low-speed ascent signal is output (see Figure 12 (a)). a)], the solenoid excitation current of the ascending electromagnetic proportional pilot valve 7 has an S-shaped pattern Yu.
(See Fig. 2(a)), and the rising control valve 2 is operated in the opening direction.As a result, the supply flow rate Qu2 to the hydraulic cylinder 6 decreases [see Fig. 18], and the rising control valve 2 is operated in the opening direction. The bleed-off flow rate Qul of the control valve 2 increases [see Fig. 13], and the cage 5 is decelerated [Fig.
See a)]. Next, the command pattern is a predetermined low-speed current Iu
i (see Fig. 2 (a)), and the vehicle enters a running state with a low speed rise, that is, the landing speed Vf [see Fig. 3 (a)]
. When the stop limit switch for floor alignment operates, the low speed rise signal of the controller 25 is also cut off [Fig. 12 (
a)], the command current follows a predetermined S-shaped command pattern Z.
u (see FIG. 2(a)), the ascending control valve 2 returns to the state shown in FIG. 8, bleeds off the entire discharge ff1Qp of the hydraulic pump 4 [see FIG. Stop [see Figure 3 (a)].In order to reduce the shock when the cage 5 stops, after the cage 5 has completely stopped, a certain short period of time has elapsed since the stop command. , the hydraulic pump 4 is stopped (see FIG. 9).

By the way, in the above operation, if the weight of the cage 5 is large and the pressure of the hydraulic oil acting on the hydraulic cylinder 6 increases, even if the lift control valve 20 is opened as instructed, the hydraulic oil will not be supplied to the hydraulic cylinder 6. This causes changes in the amount of oil and the amount of oil discharged from the hydraulic pump. The hydraulic oil bleeds off through the notch 26u formed in the valve body 18u of the ascending control valve 2, but at this time, the streamline angle θ of the hydraulic oil after passing through the notch 26u is small. The relatively large fluid reaction force generated by this causes the valve body 18u of the ascending control valve 2 to move slightly in the closing direction.

The larger the difference between the pressure P of the hydraulic oil that has flowed into the rising control valve 2 and the pressure Pt of the hydraulic oil that is being bleed off, the more the valve body 18u will close due to the fluid reaction force of the hydraulic oil. will be moved. Therefore, when many people are on board and it is necessary to increase the pressure acting on the hydraulic cylinder 6, the lift control valve 2 has a bleed-off amount determined by the shape of the notch 26u, and the amount of bleed-off to the hydraulic cylinder 6 is determined by the shape of the notch 26u. The supply amount is set to a desired value regardless of the pressure of the hydraulic oil from the hydraulic pump 4. Such operations are performed in the same way when running at full speed or at the landing speed.

The descending control valve 3 is normally closed, the valve body 18d is in a pressed state due to the action of the spring 3b, and the valve is in the 20th position.
It is fully closed as shown in the diagram. When there is a command to lower the cage 5, the hydraulic pump 4 is not driven [see Fig. 9].
Operation, high-speed descending, and low-speed descending signals are input to the controller 25 [Fig. 10 (b), Fig. 11 (b), and Fig. 1
See Figure 2 (b)]. The solenoid 21a of the electromagnetic pilot switching valve 21 is energized by the signal from the controller 25.
(See FIG. 21), the electromagnetic pilot switching valve 21 opens, and hydraulic oil flows in from the hydraulic cylinder 6 via the throttle 20, causing the pressure P in the oil passage 16 to rise (See FIG. 22). In this state, the drive current gradually increases according to the command pattern [see Fig. 2 (b)], so that the solenoid excitation of the lowering electromagnetic proportional viroft valve 10 increases, and the pressure P4 on the secondary side corresponds to its opening degree. is defined [see Figure 23]. Depending on the pressure, an amount of oil qci passing through the downstream fixed throttle 11 is generated (see FIG. 24), and a pressure difference is generated before and after the fixed throttle 12. When the opening degree of the descending electromagnetic proportional pilot valve lO changes, the differential pressure P-P3 becomes even larger,
The amount of oil passing through the lowering control valve 3 is gradually increased. That is, the solenoid excitation current of the descending electromagnetic proportional pilot valve IO increases [see Fig. 2 (b)], the pilot flow 1tqd passing through the downstream fixed throttle 11 increases [see Fig. 24], and the downstream fixed The pressure P4 on the upstream side of the throttle 11 also increases (see FIG. 23). Therefore, the pressure P in the oil passage 16 before and after the fixed throttle 12 downstream of the filter 18 interposed in the hydraulic pilot circuit branched to the oil passage 16 (see FIG. 22), and the upstream of the lowering electromagnetic proportional pilot valve 10. The differential pressure P-P3 with respect to the pressure P3 (see Figure 25) increases.Since the pressure P3 acting on the spring chamber 3A is smaller than the pressure P acting on the flow chamber 3B, the lowering control valve 3 is lowered as shown in Figure 5. Operates in the direction of opening as shown.Descent control valve 3
In response to the opening operation of the check valve 15, the check valve 15 is opened. 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. 26], and the descent of the cage 5 is accelerated. [
See Figure 3(b)]. Next, the command pattern becomes a predetermined high-speed current Idt [see FIG. 2(b)], and the cage 5 descends at a high speed Vd [see FIG. 3(b)].

When the cage 5 approaches the lower floor, the deceleration limit switch is activated and the controller's high-speed descent signal is cut off [Figure 11 (
b)], the current of the descending electromagnetic proportional pilot valve 10 is gradually decreased according to the command pattern Yd [see Fig. 2(b)].
)], the lowering control valve 3 is operated in the closing direction. Therefore, the control flow lQd of the descending control valve 3 decreases (see FIG. 26), and the cage 5 is decelerated (see FIG. 3(b)). Next, the command pattern becomes a predetermined low-speed current of 1 di [see Figure 2 (b)], and a low-speed running state occurs [3rd
See figure (b)]. When the stop limit switch for floor alignment is activated, the low-speed descending signal of the controller 25 is cut off (see Fig. 12(b)), and the command current is changed to a predetermined pattern Z.
d [see FIG. 2(b)], and the descending control valve 3 gradually closes until it is completely closed as shown in FIG. 27. In addition, in order to alleviate the shock when the cage 5 stops, the solenoid drive signal of the electromagnetic pilot switching valve 21 is activated after a certain short period of time has elapsed from the stop command after the lowering control valve 3 is completely closed. It is then shut off (see Figure 21).

Even when the cage 5 is lowered in this manner, the lowering control valve 3
The amount of oil discharged from the hydraulic cylinder 6 passing through is relatively thick due to the notch 26d.
d moves slightly in the closing direction. As a result, even if the amount of oil flowing from the descending control valve 3 to the tank 13 tends to increase due to the large pressure of the hydraulic cylinder 6, the amount of oil is restricted and the pressure of the hydraulic oil acting on the hydraulic cylinder 6 is reduced. The desired value is set regardless.

As can be seen from the above explanation, the hydraulic pilot circuit of the ascending control valve is provided with an ascending electromagnetic proportional pilot valve and a downstream fixed throttle, and the descending control valve's hydraulic pilot circuit is provided with a descending electromagnetic proportional pilot valve and a downstream fixed throttle. Since a fixed aperture is provided and an electric oven control method that does not require gain adjustment is adopted, there is no need for electrical adjustment during the initial adjustment of the device.

In addition, even if the pressure of the hydraulic oil acting on the hydraulic cylinder changes, the amount of oil supplied to the hydraulic cylinder and the amount of oil passing through the lowering control valve can be maintained at a predetermined value, allowing the cage to accelerate or decelerate. High speed and low speed running are maintained at desired values. Furthermore, the solenoid drive command signal in the ascending or descending pattern with an S-shaped curve during acceleration/deceleration is output to each of the electromagnetic proportional pilot valves, so the command signal when shifting from acceleration or deceleration to constant speed is output. is smooth,
The ride comfort of the cage is improved.

[Brief explanation of the drawing]

Fig. 1 is a circuit diagram of the hydraulic elevator valve device of the present invention;
Figures (a) and (b) are solenoid drive signal waveform diagrams of the ascending electromagnetic proportional pilot valve and the descending electromagnetic proportional pilot valve output from the opening command means;
b) is a cage vertical speed diagram, Figure 4 is a sectional view of the lifting control valve when the valve body with a notch is in the intermediate opening position, and Figure 5 is a diagram of the lift control valve when the valve body with a notch is in the intermediate opening position. Figure 6 is a cross-sectional view of the lowering control valve with a valve body without a notch, and Figure 7 is a cross-sectional view of the lowering control valve when it is in the intermediate opening position. Fig. 8 is a cross-sectional view of the ascending control valve in the fully open state; Fig. 9 is a diagram of the operating state of the hydraulic pump; Fig. 10 Figures (a), (b)
) is the operation signal input to the controller, Fig. 11 (a
), (b) are high-speed lift signals input to the controller, Figures 12 (a) and (b) are low-speed lift signals input to the controller, and Figure 13 is the state of change in the bleed-off amount in the lift control valve. Fig. 14 is a diagram of changes in the pilot control oil amount during ascending, Fig. 15 is a diagram of changes in downstream control pressure of the electromagnetic proportional pilot valve for ascending, and Fig. 16 is a diagram of changes in pressure in the oil path downstream of the hydraulic pump. Figure 17 is a diagram of changes in the pilot control pressure of the lift control valve, Figure 18 is a diagram of changes in the amount of hydraulic oil supplied to the hydraulic cylinder, and Figure 19 is a diagram of changes in the amount of hydraulic oil supplied to the hydraulic cylinder.
The figure shows a sectional view of the ascending control valve in the fully closed state, Fig. 20 shows the sectional view of the descending control valve in the fully open state, Fig. 21 shows the opening state of the electromagnetic pilot switching valve, and Fig. 22 shows the hydraulic cylinder. Fig. 23 is a diagram of changes in pressure in the return oil path from , Figure 23 is a diagram of changes in downstream control pressure of the descending electromagnetic proportional pilot valve,
Figure 24 is a diagram of changes in pilot control oil amount during descent;
Fig. 25 is a diagram of changes in the pilot control pressure of the descending control valve, Fig. 26 is a diagram of changes in the controlled amount by the descending control valve during descent, and Fig. 27 is a cross-sectional view of the descending control valve in the fully closed state. ,
FIG. 28 shows an example of a hydraulic elevator valve device in the prior art using electrical feedback control, and FIG. 29 (a
) and (b) are speed change diagrams of the cage moving up and down. 2-・Rising control valve, 2A-pilot chamber (spring chamber),
3...-Downward control valve, 3A-Pilot chamber (spring chamber)
, 4-hydraulic pump, 5...cage, 6-actuator (hydraulic cylinder), 7...electromagnetic proportional pilot valve for ascending, 8--downstream fixed throttle, 9-fixed throttle, 10--
Lowering electromagnetic proportional pyloft valve, 11-downstream fixed throttle, 1
2-Fixed aperture, 18.18'u. 18d--Valve body, 24--Opening command means, 26.26u
, 26d--all missing, Pl, P3--pilot pressure. Patent distributor Kawasaki Heavy Industries Co., Ltd. Agent
Patent Attorney Katsutoshi Yoshimura (1 person) Figure 7 Figure 1 Gildan Eye Hair Pressure Figure 13 Figure 15 Figure 16 Figure 18 Figure 22 Figure 23 Figure 21 + Figure 25 Figure jff Figure 26

Claims (1)

[Claims] A normally open ascending control valve and a normally closed descending control valve are provided, and the opening degree of each valve is adjusted to control the amount of oil from a hydraulic pump or actuator. , in a hydraulic elevator valve that maintains the speed of the cage at a command value, a hydraulic pilot circuit of the above-mentioned ascending control valve is provided with an ascending electromagnetic proportional pilot valve and a downstream fixed throttle; A fixed throttle is installed that generates pilot pressure from the generated flow and applies that pressure to the pilot chamber of the ascending control valve.A descending electromagnetic proportional pilot valve and a downstream fixed throttle are installed in the hydraulic pilot circuit of the descending control valve. At the same time, a fixed throttle is provided that generates pilot pressure by the flow generated in the hydraulic pilot circuit, and applies that pressure to the pilot chamber of the lowering control valve, so that the solenoid drive signal of the ascending or descending command pattern is transmitted. ,
An opening command means for outputting to each electromagnetic proportional pilot valve is provided, and a notch is formed in the valve body of the ascending control valve and descending control valve, and the notch is inclined or A hydraulic elevator valve device characterized by having an arc shape.