JPH01229103A - Double diffuseness type hydraulic operating device - Google Patents

Abstract

PURPOSE:To make it possible to continue the drive of a operated body by parallelly connecting the operating portion of a hydraulic cylinder to the operated body, providing a pressure compensator in a return pipe and providing an inoperative trouble detecting device at a servo valve. CONSTITUTION:Operating portions 4a, 4b consisting of double acting hydraulic cylinders 6a, 6b servo valves 7a, 7b and bypass valves 9a, 9b are parallelly connected to an operated body 1 and a pressure compensator for rising the pressure of return operating oil is provided in a return pipe. Servo valve inoperative trouble detectors 35, 36, 37 operated by the excessive operating force of the servo valve 7a are provided between the spool 12, the link 13 of the servo valve 7a and an arm 34. Accordingly, when the servo valve 7a is out of order, a trouble is thereby detected in a moment through an operator's counter pressure operation and it is possible to be switched to the other servo valve 7b so that the drive of the operated body can be continued.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a hydraulic actuator including a hydraulic cylinder for driving a control surface of an aircraft or other flying object, a landing gear, or an industrial equipment requiring high reliability. Concerning this.

Conventional technology In the conventional force summing type drive device in which two hydraulic cylinders are connected in parallel to the actuated body, slight misalignment of the hydraulic cylinders and related components (misalignment) and the mounting parts of both hydraulic cylinders are common. Due to the difference in rigidity between the servo valves, there is a difference in the movement of each servo valve in response to the input amount, and this causes severe interference between the operating forces (force fight) between the two sleeve pressure cylinders, resulting in a reduction in the output of the drive device and performance deterioration. There was a problem of causing such problems. In order to prevent force fights, a link with a complicated structure is required, but this increases the size of the device and reduces reliability, which is undesirable.

Furthermore, in the above-described structure in which the hydraulic cylinders are installed and one hydraulic cylinder is used as the always-operating side, and the hydraulic knolling of the other power is switched and used as the standby side, the standby-side hydraulic cylinder is dragged by the always-active side hydraulic cylinder. Since the cylinder is moved, the hydraulic oil inside the cylinder is discharged, causing internal lubrication failure, which deteriorates the durability of internal parts such as the cylinder seal. Since there was no simple and highly reliable fault detection means for detecting a non-operational fault when it occurred, no effective fault countermeasures could be taken.

Problems to be Solved by the Invention It is an object of the present invention to solve the above-mentioned conventional problems, and therefore, an object of the present invention is to provide a double redundant hydraulic actuating device that solves these problems.

Means for Solving the Problems In order to achieve the above object, the hydraulic actuating device of the present invention includes an operating portion of a double-acting hydraulic cylinder that can independently actuate an actuated body operated by the hydraulic actuating device, and an actuating portion for the hydraulic cylinder. A pair of hydraulic cylinders with servo valves are integrally connected to the main body of the servo valve, and the operating amount of the actuating part is negatively fed back to the opening degree of the servo valve.The operating parts of the hydraulic cylinders are connected in parallel to a common actuated body; An electromagnetic switching valve that switches the hydraulic pressure supply to each hydraulic cylinder, and /lIl on both sides of the piston of each double-acting hydraulic cylinder.
A bypass valve that shuts off or communicates between the chambers depending on the presence or absence of supplied hydraulic pressure, a pressure compensator that is located in the pipeline from the electromagnetic switching valve to the hydraulic pressure source and that increases the pressure of the return hydraulic oil from the servo valve, and a servo valve. The present invention has a dual redundant hydraulic actuator configuration, which is equipped with a servo valve inoperation failure detector that is actuated by excessive valve operating force to generate an electric signal for switching the electromagnetic switching valve.

Function: The back of the pair of hydraulic cylinders with servo valves, the double-acting hydraulic cylinder to which hydraulic pressure is supplied from the electromagnetic switching valve, has communication between the oil chambers on both sides of the piston cut off due to the operation of the bypass valve. The double-acting hydraulic cylinder, which is in a state where it can be operated by the servo valve but is not supplied with oil pressure by the electromagnetic switching valve, has oil chambers on both sides of the piston communicating with each other due to the bypass valve, and the servo valve opens and closes. It is in a state where it can move back and forth regardless of the situation.

If you operate the control stick, for example, forward in the above state, both servo valves open simultaneously in the same direction, but hydraulic oil flows into the hydraulic cylinder from the servo valve to which hydraulic pressure is supplied, causing its operating part to move forward. .

The actuated body is driven in a predetermined direction by this movement of the actuating part, but the amount of movement of the actuating part is negatively fed back to the servo valve to reduce its opening, so the moving speed of the actuated body gradually decreases. , it is finally positioned and stopped at a predetermined position.

During the movement, the waiting hydraulic cylinder to which no hydraulic pressure is supplied can move freely, so it follows the operating part, and the return oil of the operating hydraulic cylinder is increased in pressure by the pressure compensator. and is guided to the waiting hydraulic cylinder to lubricate the inside of the hydraulic cylinder.

In the above state, if the servo valve of the operating hydraulic cylinder is in an open state and fails to operate (sticks), the hydraulic cylinder runs out of control to the end of its stroke. At this time, when the control tool fixes or moves the control stick by a counter operation, an excessive operating force is applied to the servo valve, and the servo valve malfunction detector emits an electric signal to switch the electromagnetic switching valve. As a result, the hydraulic pressure supply to the failed hydraulic cylinder is stopped, and the bypass valve is restored and becomes free to move.

At the same time, hydraulic pressure is supplied to the standby hydraulic cylinder through the servo valve, and at the same time, the bypass valve is operated to return the hydraulic cylinder to the operating state and operate the actuated body in place of the failed hydraulic cylinder. Thereafter, the return oil from the other hydraulic cylinder flows into the failed hydraulic cylinder to perform lubrication in the same manner as described above.

Embodiment FIGS. 1 and 2 show an embodiment in which the present invention is applied to the operation of a control surface of an aircraft. Both ends of the front edge 1a of the actuated body (control surface) 1 are pivotably supported by a fixed bracket 2 for free tilting, and a pair of actuating parts 4a and 4b protrude from the lower part of an arm 3 rising from both ends. The portion 5 is pivotally mounted so that it can move freely up and down. On each operating part 4a, 4b, there is a pair of servo valve equipped hydraulic cylinders 8a, 8b, each consisting of a double acting hydraulic cylinder 6a (or 6b) and a servo valve 7a (or 7b) parallel to the double acting hydraulic cylinder 6a (or 6b) at a constant interval. and each of the bypass valves 9a, 9b are fixed. The piston ronds 10.10 of the hydraulic cylinders 6a, 6b are approximately on a line passing through the pivot point of the arm 3 and the protrusion 5, and their front ends are pivoted to a fixed bracket 11, respectively, and a servo valve 7a.

The front ends of the spools 12.12 of 7b are connected to the respective actuating parts 4a,
The lower end of the link 13 is pivotally connected to the front part of the link 4b, and is connected to the middle part of the link 13.

Pipe lines 16, 17 connected to the ends of the oil chambers 14, 15 of the hydraulic cylinders 6a, 6b are connected to servo valves 7a, 7, respectively.
b, and the opening is closed when the spool 12 is in the neutral position. Furthermore, when the spools 18 of the bypass valves 9a and 9b are retracted to the illustrated position by the springs 19, the pipes 20 and 21 branched from the pipes 16 and 17 are connected by the passage 22 in the spool 18, and the hydraulic cylinder 6a, 6b can be moved freely back and forth.

The hydraulic oil discharged from the hydraulic source 23 is transferred to the electromagnetic directional control valve 24.
For example, the spool 18 of the bypass valve 9d is advanced against the spring 19, and the communication between the lines 20 and 21 is cut off. Therefore, when the link 13 is next tilted forward or backward by an operation from the cockpit, the servo valve 7a opens and the hydraulic oil flows into the pipe 16.
Or it flows into the hydraulic cylinder 6a from 17, and the actuating part 4a
move forward or backward. At this time, the hydraulic cylinder 6b to which hydraulic oil is not supplied can freely move back and forth because its pipe lines 16 and 17 are in communication, and therefore, the actuating part 4b also moves back and forth due to the back and forth movement of the actuating part 4a. Follow and move back and forth.

The moving speed of the actuating parts 4a, 4b is determined by the opening degree of the servo valve 7a, and although it is relatively thick at the initial stage of operation, the lower end of the link 13 moves due to the back and forth movement of the actuating part 4a, and the spool 12 moves towards the servo valve 7a. The actuating portion 4a decelerates and finally stops. That is, the actuated body 1 is positioned and stopped at an accurate predetermined tilting position by the negative feedback effect caused by the movement of the actuating portion 4a.

During the above movement, the hydraulic oil discharged from the hydraulic cylinder 6a to the discharge pipe 2La via the servo valve 7a is applied to a predetermined back pressure by a check valve or pressure compensator 28 provided between the electromagnetic switching valve 24 and the hydraulic power source 23. The oil is pressurized and guided from the discharge pipe 27b through the servo valve 7b into the hydraulic cylinder 6b to perform internal lubrication and maintain durability such as corrosion protection of the rail and internal parts.

In the above state, if the servo valve 7a is open and malfunctions, the hydraulic cylinder 6a
Depending on the position a, the stroke will run out of control to either end of the stroke. At this time, when the control stick 29 is fixed or actuated by a counter operation of the control tool, the torque tube 30 interlocked with the control stick 29, the sector 31 and the chain 32 fixed thereto.
When the control rod operation force is applied to the sector 33 and the arm 34, the override device (Pansy Rondo) 35 provided between the arm 34 and the tip of the link 13 is extended or contracted, and one of the springs 36 is bent, causing a malfunction. The detection switch 37 detects this and switches the electromagnetic directional switching valve 24 based on the electrical signal. As a result, the hydraulic pressure supply to the servo valve 7a is cut off, and the hydraulic pressure is supplied to the servo valve 7b, so that the hydraulic cylinder 6b enters the operating state in place of the hydraulic cylinder 6a.

On the thus disconnected hydraulic cylinder 6a side, the pipe line 16. ] 7 communicate with each other, and the oil in the hydraulic cylinder 6a can return to the hydraulic source 23 from the oil drain pipe 27a, so the hydraulic cylinder 6a does not cause hydraulic lock, and the actuating part 4a follows the actuating part 4b. do. Further, the inside of the hydraulic cylinder 6a is lubricated in the same manner as described above.

Even when one of the servo valves 7a, 7b becomes inoperable due to breakage of the operating mechanism, switching and lubrication of the failed hydraulic cylinder are performed in exactly the same manner as described above.

Effects of the Invention Since the present invention has the above-mentioned configuration, normally the actuated body is driven by the hydraulic cylinder with the servo valve that is normally in operation, and when the servo valve of one of the hydraulic cylinders is inoperable, the operation is stopped. It is possible to detect an instantaneous failure by countermanipulation by a person and switch to the hydraulic cylinder with a servo valve on the standby side to continue driving the actuated body.In addition, the return oil of the hydraulic cylinder to which hydraulic pressure is being supplied can be transferred to the hydraulic cylinder with a servo valve on the standby side. It has excellent effects such as being able to lead to a hydraulic cylinder and lubricate the inside of the hydraulic cylinder, thereby maintaining the durability of its seals and internal parts.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention; FIG. 1 is an overall configuration diagram including a hydraulic circuit, and FIG. 2 is an overall configuration diagram including a servo valve operating mechanism. 1. Actuated body 4a, 4b. Actuating part 5... Projection part 6a, 6b... Double acting hydraulic cylinder 7a, 7b... Servo valve 8a, 8b... Hydraulic cylinder with servo valve 9a.
, 9b...Bypass valves 14, 15...Oil chamber 23 Hydraulic source 24...Solenoid switching valve 28...Pressure compensator 35, 36.37...Servo valve inoperation failure detector Fig. 1

Claims (1)

[Claims] A pair of servos, in which the actuating part of a double-acting hydraulic cylinder capable of independently actuating an actuated body and the main body of a servo valve for the cylinder are integrally connected, and the actuating amount of the actuating part is negatively fed back to the opening degree of the servo valve. The operating parts of the hydraulic cylinders with valves are connected in parallel to a common actuated body, and an electromagnetic switching valve switches the hydraulic pressure supply to each double-acting hydraulic cylinder, and the oil chambers on both sides of the piston of each double-acting hydraulic cylinder are supplied respectively. A bypass valve that shuts off or communicates depending on the presence or absence of hydraulic pressure, a pressure compensator that increases the pressure of the return hydraulic oil from the servo valve in the return line from the electromagnetic switching valve to the hydraulic source, and excessive operating force of the servo valve. A double redundant hydraulic actuator equipped with a servo valve inoperation failure detection device that is activated by the servo valve to generate an electric signal for switching the electromagnetic switching valve.