JP2002349513A - Actuation system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an actuation system at low cost and with an excellent flying safety by introducing such a structure that a requisite fluid amount and fluid pressure to an actuator is secured when the externally supplied pressure has sunk, without using any additional fluid source provided externaly. SOLUTION: An internal fluid source 40 to supply a working fluid having a specified supply pressure is connected to supply/exhaust passages 23 and 28 for the working fluid leading to the actuator 10 from the external fluid source, and an internal supply pressure lead-in port 43 to lead in the working fluid from, the internal fluid source 40 is formed separately from an external supply pressure lead-in port 21 to lead in the working fluid having the specified supply pressure from the external fluid source, and the working fluid is supplied from the external supply pressure lead-in port 21 and internal supply pressure lead-in port 43 to a mechanical control valve 31 and an electrical control valve 32.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to an actuation system using a fluid pressure actuator, and more particularly to an actuation system in which a fly-by-wire type control device is provided with a mechanical control mechanism.

[0002]

2. Description of the Related Art Conventionally, control surfaces of an aircraft (elevation, rudder,
Fly-By-W (Fly-By-W) that controls a controlled object such as a flight control wing surface such as an aileron without relying on mechanical linkage
ire: hereinafter referred to as FBW) type control system has been realized. However, in an aircraft or the like that requires a high level of safety and reliability for respecting human life, an electric system that makes FBW control impossible. It is necessary to be able to control the control surface in response to a manual operation input from the control stick even when a failure occurs. Therefore, in such a case, the input link and the control stick provided in the supply / discharge control mechanism of the hydraulic actuator are mechanically connected by a relatively simple linkage, so that mechanical control can be performed mechanically. Some have a mechanism.

In a normal FBW mode, a flight control computer (Flight Control Computer) of an aircraft is used.
r: Hereinafter, simply referred to as FCC) is a stability increasing device (SAS: S
tability Augmentation System)
An input command is generated by adding a correction value and the like for stabilizing the aircraft to the operation command by the control stick, and this command signal is input to the electro-hydraulic servo circuit to supply and discharge hydraulic oil to the control surface control actuator. Is controlled to control the steering and steering of the control surface.

On the other hand, if the FBW mode of one of a plurality of systems cannot be used, for example, if the supply pressure from a fluid source drops below a predetermined pressure or the electric circuit of one of the systems fails, a failure occurs. It is necessary to ensure that the actuators in the system do not adversely affect the normal operation of the actuators in the other system. It is possible to switch to a mode having a so-called bypass function in which there is no resistance. further,
In the case where all the supply pressures of a plurality of systems fail, in order to prevent flutter on the control surface, a throttle element is inserted between the supply-side and discharge-side fluid chambers to provide a so-called damping function. ing.

[0005]

However, in the above-mentioned conventional actuation system, the supply pressure is reduced due to the failure of the external fluid supply source (the supply source of the fluid pressure) or the decrease of the inflow amount, and the safety is reduced. Even if the air pressure drops, it is not possible to directly compensate for the drop in the supply pressure, etc., to generate the required fluid volume and fluid pressure. This was a problem to be solved.

[0006] On the other hand, for example, it is conceivable to add an external fluid source. However, adding an external fluid source at the same level as a normal external fluid source used at the time of FBW control is not only in terms of cost, but also There was also a problem with the weight of the system.

Accordingly, the present invention is to provide a low-cost, high-flying-safety vehicle that can secure a required fluid amount and fluid pressure to an actuator when an external supply pressure is reduced without adding an external fluid source. It is an object of the present invention to provide an actuation system.

[0008]

In order to solve the above problems, the present invention forms one and other fluid chambers on both sides of a piston housed in a cylinder, and supplies a working fluid to both fluid chambers. An actuator for moving a piston by discharging, a supply / discharge control mechanism having a control valve for controlling supply and discharge of a working fluid from a predetermined external fluid source to the one and the other fluid chambers, and operating the control valve And a mode switching valve for switching a control mode of the supply / discharge control mechanism, wherein a working fluid of a predetermined supply pressure is connected to a supply / discharge passage of a working fluid from the external fluid source to the actuator. An internal fluid source is provided to supply a working fluid at a predetermined supply pressure from the external fluid source, separately from an external supply pressure introduction port. To form the internal supply pressure inlet port for introducing the working fluid, and supplies the working fluid to said control valve from the external supply pressure inlet port and an internal supply pressure introduction port.

In this system, an internal fluid source is connected to a supply / discharge passage of a working fluid from an external fluid source to an actuator, and the internal fluid source is provided separately from an external supply pressure introducing port for introducing a working fluid from the external fluid source. An internal supply pressure introduction port for introducing a working fluid from the inside is formed, and the working fluid is supplied to the control valve from both the external and internal supply pressure introduction ports. Therefore, when the supply pressure and the supply amount from the external fluid source decrease, the internal fluid source can be operated to compensate for the decrease, and flight safety can be ensured.

Further, the present invention provides an actuator which forms one and the other fluid chambers on both sides of a piston housed in a cylinder, and moves the piston by supplying and discharging a working fluid to and from the two fluid chambers; A mechanical control valve that is switched by an operation input; and an electric control valve that is switched by a steering electric signal input. And a supply / discharge control mechanism for controlling discharge and a supply / discharge passage for supplying and discharging a working fluid from a predetermined external fluid source to the actuator, and any one of the mechanical control valve and the electric control valve. Select and insert,
A mode switching valve for switching a control mode of the supply / discharge control mechanism, and an operating force transmitting member for transmitting an external mechanical operation input to the mechanical control valve, wherein the mode switching valve causes the mechanical control valve to A mechanical control mechanism that, when inserted into the supply / discharge passage of the working fluid to the actuator, activates the mechanical control valve by an operation input via the operation force transmission member, the actuation system comprising: An external fluid source connected to a supply / discharge passage of a working fluid from an external fluid source to the actuator, for supplying a working fluid at a predetermined supply pressure, and introducing a working fluid at a predetermined supply pressure from the external fluid source In addition to the pressure introduction port, an internal supply pressure introduction port for introducing a working fluid from the internal fluid source is formed, and the external supply pressure introduction port and the internal supply pressure introduction port are formed. It is from the internal supply pressure introduction port that form a passage for supplying hydraulic fluid to said mechanical control valves and electric control valve.

In this system, an internal fluid source is connected to a supply / discharge passage of a working fluid from an external fluid source to the actuator, and the internal fluid source is provided separately from an external supply pressure introducing port for introducing a working fluid from the external fluid source. An internal supply pressure introduction port for introducing a working fluid from the outside is formed, and the working fluid is supplied to the mechanical control valve and the electric control valve from both the external and internal supply pressure introduction ports. Therefore, when the supply pressure and the supply amount from the external fluid source decrease, the internal fluid source can be operated to compensate for the decrease, and flight safety can be ensured.

[0012] The actuation system of the present invention comprises:
Further, the supply of the working fluid from the external supply pressure introduction port and the internal supply pressure introduction port to the mechanical control valve and the electric control valve is permitted, while the external supply pressure is supplied from the mechanical control valve and the electric control valve. It is preferable that a check valve be provided to prevent backflow to the pressure introduction port and the internal supply pressure introduction port. In this case, when the introduction pressure on the external supply pressure introduction port side decreases, the working fluid pressure exceeding the introduction pressure on the external supply pressure introduction port side is applied from the internal supply pressure introduction port side to the mechanical control valve and the electric control valve. Can be supplied.

Further, the actuation system of the present invention allows the supply of the working fluid from the external supply pressure introduction port to the mechanical control valve, while allowing the mechanical control valve to supply the working fluid to the external supply pressure introduction port. A check valve for preventing backflow of the fluid, and configured to allow a backflow of the working fluid to the external supply pressure introduction port side only from the electric control valve among the mechanical control valve and the electric control valve. I can do it. With this configuration, when the introduction pressure on the external supply pressure introduction port side decreases, the working fluid pressure exceeding the introduction pressure on the external supply pressure introduction port side is supplied from the internal supply pressure introduction port side to the mechanical control valve. On the other hand, when a large load pressure acts on the electric control valve from the actuator side, the backflow of the working fluid to the external supply pressure introduction port side is allowed.
Therefore, it is possible to prevent an excessive force from being applied to the support portion of the actuator.

The actuation system of the present invention comprises:
Further, a relief valve set at a predetermined discharge pressure is provided in the discharge passage of the working fluid, and the internal fluid source pressurizes the working fluid from the discharge passage of the working fluid to supply the working fluid at the predetermined supply pressure. A configuration having a supply pump may be employed. In this case, a constant back pressure can be applied to the pump of the internal fluid source according to the set pressure of the relief valve arranged in the discharge passage, and the required internal pressure of the internal fluid source can be maintained regardless of the operation state of the actuator. The supply pressure can be generated in a timely manner.

Further, in the actuation system of the present invention, a working fluid is introduced from the external supply pressure introduction port, and an operation pressure for switching a control mode of the supply / discharge control mechanism by the mode switching valve is controlled. Preferably, a switching operation pressure control means is provided. In this case, the operation mode of the actuator can be switched to a preferable mode when the supply pressure from the external fluid source is lost.

[0016]

Preferred embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) FIGS. 1 and 2 are views showing an actuation system according to a first embodiment of the present invention. In the present embodiment, the present invention is applied to each of multiple parallel hydraulic control systems, and the drawing shows only one system. The configuration described below is common to each control system that drives the same control surface.

First, the configuration will be described. In FIG. 1, 1
Numeral 0 denotes a hydraulic actuator, and the actuator 10 has a cylinder 11 and a piston 12. The actuator 10 includes one and the other oil chambers 13, 1 on both sides in the axial direction of a piston 12 housed in a cylinder 11.
4 (fluid chamber), and hydraulic oil (operating fluid) is supplied to one of these two oil chambers 13 and 14 and discharged from the other, thereby applying hydraulic pressure to the piston 12. The piston 12 is moved.
The actuator 10 is swingably supported by an aircraft body side structural member 1 (not shown) by a bracket portion 10a, and a rod portion 12e of a piston 12 is connected to a control surface side member W of the aircraft.

The oil chambers 13 and 1 of the actuator 10
Hydraulic oil is supplied to and discharged from a supply / discharge control mechanism 20 to be described later, and an external fluid supply source (external fluid source) (not shown) for supplying a hydraulic oil having a supply pressure P to the supply / discharge control mechanism 20.
And a reservoir circuit (or a tank) for storing the hydraulic oil discharged from the actuator 10 and returning it to the external fluid supply source side. In addition, for example, a check valve and a filter (not shown) are provided between the external supply pressure introduction port 21 of the supply and discharge control mechanism 20 and the external fluid supply source.

Reference numeral 25 denotes an input link which responds to a mechanical operation input. The input link 25 is constituted as a swing type operation force transmitting member capable of inputting an operation force from both upper and lower ends in FIG. ing. That is, the first moving end portion 25a (the upper end portion in FIG. 1) of the input link 25 is connected to a manual operation member such as a control stick or a pedal (not shown) operated by a pilot via a mechanical linkage, The second moving end 25b (the lower end in FIG. 1) of the input link 25 is swingably supported by the rod 12e of the piston 12. The input link 25 has a summing point 25c (valve operation point) between the two moving ends 25a and 25b, and the manual operation amount from the first moving end 25a and the summing point 25c from the second moving end 25b. A mechanical displacement corresponding to a deviation from the mechanical feedback amount is output from the summing point 25c as a valve operation amount.

Reference numeral 31 denotes a mechanical control valve which can be switched between three positions and whose four ports are opened and closed and the opening is adjusted by the input link 25. The mechanical control valve 31 includes a supply pressure port 31 a connected to a supply passage 23 from the external supply pressure introduction port 21, and a drain connected to the reservoir circuit via a discharge passage 28 and a discharge port 29 to the outside. It has a port 31b and a pair of control pressure ports 31c, 31d connected to both ports in response to an operation input. The mechanical control valve 31 supplies the hydraulic oil from the external fluid supply source to the oil chamber 13 or 14 through the supply pressure port 31a and the control pressure port 31c or 31d, and the hydraulic oil from the oil chamber 14 or 13 The drain port 3
1b, and furthermore, the connection between the supply pressure port 31a and the drain port 31b and the control pressure ports 31c, 31d is cut off to stop the supply and discharge of the hydraulic oil to the oil chambers 13, 14. Can be. In FIG. 2, reference numeral 31e denotes a valve body of the mechanical control valve 31, and reference numeral 31h denotes a substantially sleeve-shaped operation input section in which the ports 31a, 31b, 31c, and 31d are formed.
The operation input unit 31h relatively moves with the valve body 31e in response to an operation input from the input link 25, and the ports 31a,
The degree of opening of 31b, 31c and 31d can be changed.

Reference numeral 32 denotes an electric control valve which is electromagnetically driven to open and close four ports and adjusts the opening degree by electric control signals Sa and Sb, which are steering control signals from an FCC (not shown), and which can switch between three positions. is there. This electric control valve 32
Are connected to a supply pressure port 32a for introducing hydraulic oil from a fluid pressure supply source, a return port 32b for discharging hydraulic oil to a reservoir circuit, and both ports 32a and 32b in response to input of control signals Sa and Sb. Control pressure port 3
2c and 32d. Also, the electric control valve 32
The hydraulic pressure is applied to the oil chamber 13 or 14 through the pair of control pressure ports 32c and 32d according to the signal level of the electric control signal Sa or Sb, for example, by electromagnetically driving the valve body 32e according to the electric control signals Sa and Sb. Hydraulic oil from the supply source can be supplied and hydraulic oil from the oil chamber 14 or 13 can be discharged to the reservoir circuit through the return port 32b. Further, the electric control valve 32
The connection between the supply pressure port 32a and the return port 32b and the control pressure ports 32c and 32d is cut off to
Supply and discharge of hydraulic oil to and from the pump 14 can be stopped. The electric control signal Sa is, for example, a signal in the direction of increasing the steering angle, and the electric control signal Sb is, for example, a signal in the direction of decreasing the steering angle. Each of the electric control signals is an electric control signal corresponding to the steering amount. The signals are input to the units 32j and 32k.

The one and other oil chambers 13 and 14 of the actuator 10 are controlled by a mode switching valve 33 which is a 6-port 2-position switching valve to control one of the control pressure ports 31c and 31d of the control valves 31 and 32. Or 32c, 3
2d. The mode switching valve 33 is connected to the control pressure port 3 of each of the control valves 31 and 32.
1c, 31d and a pair of control valve side ports 33a, 33b and 33c, 33d connected to 32c, 32d, respectively.
And a pair of actuator-side ports 33f, 33g connected to one and the other oil chambers 13, 14, and a pilot pressure introducing portion 33h.

The mode switching valve 33 includes a valve body 33j that is displaced in accordance with the urging force from the pilot pressure introduction part 33h, and a spring 33k that urges the valve body 33j in a direction opposite to the pilot pressure introduction part 33h. Any one of the control valves 31, 32 is controlled by one of the control pressure ports 31 c, 31 d or 32 c, 32 d by the urging force.
Mode switching valve 3 so that it can be connected to
Reference numeral 3 denotes a switch between the two supply / discharge mode positions shown in FIGS. 1 and 2, respectively.

The pilot pressure Pa applied to the pilot pressure introducing portion 33h of the mode switching valve 33 is controlled by the solenoid valve 35.
Is ON (FIG. 1), the supply pressure P from the fluid pressure supply source
When the solenoid valve 35 is OFF (FIG. 2), the pressure drops to a low pressure on the return side (back pressure by the reservoir circuit). The solenoid valve 35 is connected to the high pressure side inlet port 3 connected to the supply pressure ports 31a and 32a of the control valves 31 and 32.
5a and the drain ports 31b, 3 of the control valves 31, 32
2b and the two inlet ports 35b in response to a mode switching control signal Sc from the FCC.
a and 35b, and an outlet port 35c connected to one of the outlet ports 35a and 35b. The solenoid valve 35 includes a valve element 35d, a spring 35e, and an electromagnetic drive section 35f. When the switching control signal Sc is input to the electromagnetic drive section 35f, the valve element 35d is moved from the OFF position shown in FIG. After being displaced to the ON position, the pilot pressure Pa is applied to the mode switching valve 33 through the outlet port 35c. That is, the solenoid valve 35 is connected to the FCC.
Operating pressure supplied to the pilot pressure introducing portion 33h of the mode switching valve 33 as the pilot pressure Pa by using the hydraulic pressure of one of the fluid pressure supply source and the reservoir circuit in accordance with the mode switching control signal Sc from It is a control means.

On the other hand, the supply passage 23 and the discharge passage 28 for the hydraulic oil to the actuator 10 through the mechanical control valve 31
At least one of the passages is provided with an internal fluid pressure supply source 40 (internal fluid source) capable of increasing and controlling the flow rate and pressure of the hydraulic oil passing through the supply passage 23.

The internal fluid pressure supply source 40 is a variable capacity capable of sucking and pressurizing the working fluid from the reservoir circuit side through the working fluid discharge passage 28 and supplying the working fluid at the predetermined supply pressure. Pump 41 and an electric motor 42 that drives and controls the pump 41 in a case described below, such as when the pressure P of the working fluid (pressure oil) from the external fluid supply source is reduced. Supply passage 23 in 20
Above, an internal supply pressure introduction port 43 communicating with a discharge port (not shown in detail) of the pump 41 is formed. Here, the pump 41 is connected to one or both of the supply and discharge passages of the working fluid from the external fluid supply source to the actuator 10, for example, to both the supply passage 23 and the discharge passage 28. By connecting the internal fluid pressure supply source 40 to the supply passage 23 and the discharge passage 28, a self-actuation system (for example, a system in which a plurality of parallel hydraulic actuators are unitized)
, A working fluid of a predetermined supply pressure is supplied to the actuator 1
It can be supplied to the 0 side.

The discharge capacity of the pump 41 of the internal fluid pressure supply source 40 increases only when the internal supply pressure is generated, and is normally suppressed to a predetermined discharge capacity close to the minimum. Also, the internal fluid source 4
The zero pump 41 sucks the working fluid from the working fluid discharge passage 28, pressurizes the working fluid, and supplies the working fluid at a predetermined supply pressure to the internal supply pressure introduction port 43.

In FIG. 1, reference numeral 15 denotes a differential transformer as piston position detecting means, which is a detecting coil portion 15a housed in the cylinder 11, and an iron core (not shown) mounted on the inner end of the piston 12. And a detection core.

Next, the operation of the above-described actuation system will be described.

In the present system, the normal F is supplied while the supply pressure and the supply amount from the external fluid supply source are sufficiently secured.
BW control is performed, and the pilot's operation burden is reduced. In the FBW control mode, the internal fluid pressure source 40
Need not be operated, and the motor 42 does not rotate.

On the other hand, if for some reason the supply pressure or the supply amount from the external fluid supply source drops in a certain actuator control system, for example, it is not necessary to switch to the bypass mode. If a leak occurs in the path, the FCC side monitoring the supply pressure from the external fluid supply source operates the internal fluid pressure supply source 40 to compensate for the decrease in the external supply pressure introduction port 21. That is, the actuator 1 in the system
Zero working fluid pressure is ensured to ensure flight safety. At this time, the pump 41 is controlled to increase the discharge capacity,
The motor 42 is driven to increase the fluid pressure of the internal fluid pressure supply port 43 to a predetermined fluid pressure supply level.

As described above, in this embodiment, since the internal fluid pressure supply source 40 is connected to the supply / discharge passages 23 and 28, the external supply pressure introduction port 21 for introducing a working fluid from the external fluid supply source is connected to the external fluid pressure supply port 21. Separately, since an internal supply pressure introduction port 43 for introducing a working fluid from the internal fluid pressure supply source 40 is formed, the mechanical control valve 31 and the electric The working fluid can be supplied to the type control valve 32.

(Second Embodiment) FIG. 3 is a view showing an actuation system according to a second embodiment of the present invention. Note that, for each of the following embodiments, the above-described first embodiment will be described.
Similar to the actuation system according to the embodiment,
Since the actuator is provided with the above-described actuator 10, in the following description, the same components as those in the above-described embodiment are denoted by the same reference numerals as in FIGS. 1 and 2, and differences from the above-described embodiment are described in detail. I do.

As shown in FIG. 3, in the system of this embodiment, the mechanical control valve 31 and the electric control valve 3 are connected to the external supply pressure introduction port 21 and the internal supply pressure introduction port 43.
2, while the mechanical control valve 3
1 and external supply pressure introduction port 2 from electric control valve 32
1 and a pair of check valves 51 and 52 for preventing backflow to the internal supply pressure introduction port 43 side.

The check valve 51 opens and closes in accordance with the pressure difference between the front and rear oil passages L1 and L2 constituting a part of the supply passage 23, and the upstream oil passage L1 is separated from the downstream oil passage L2. In the case of high pressure, the valve is opened by the pressure difference between the front and rear oil passages L1 and L2 to form a free flow path, and the working fluid (pressure oil) from an external supply source to the mechanical control valve 31 and the electric control valve 32 ) Allows flow in the feed direction. Conversely, when the upstream oil passage L1 is lower in pressure than the downstream oil passage L2, the valve is closed by the differential pressure between the front and rear oil passages L1, L2, and the mechanical control valve 31 and the electric control valve 3 are closed.
The valve can be closed to prevent the backflow of the working fluid (pressure oil) from the second side to the external supply side.

The check valve 52 includes an oil passage L3 connected to the supply passage 23 and an oil passage L4 connected to the discharge port of the pump 41.
When the oil passage L3 on the pump 41 side is higher in pressure than the oil passage L4 on the supply passage 23 side, the valve is opened by the differential pressure between the front and rear oil passages L3 and L4 to open and close the free passage. Form a path,
From the pump 41 to the mechanical control valve 31 and the electric control valve 3
2 is allowed to flow in the supply direction of the working fluid (pressure oil).
Conversely, when the oil passage L3 on the pump 41 side is lower in pressure than the oil passage L4 on the supply passage 23 side, the valve is closed by the differential pressure between the front and rear oil passages L3 and L4, and the mechanical control valve 31 and the electric control Valve 3
Backflow of the working fluid (pressure oil) from the second side to the pump 41 side can be prevented.

In the actuation system of this embodiment configured as described above, in a normal FBW control state, the external supply pressure introduced into the system is directly applied to the discharge port of the pump 41 of the internal fluid pressure supply source 40. And the internal fluid pressure supply 40 can be activated only when needed.

On the other hand, when the introduction pressure on the side of the external supply pressure introduction port decreases for some reason, the decrease in the pressure monitors the introduction pressure of the external supply pressure introduction port 21 of each system, that is, the external supply pressure to each system. The pressure is detected by a pressure sensor (not shown), and is detected on the FCC side. Then, in response to the decrease in the pressure path, the motor drive signal Si is given to the motor 42, the pump 41 rotates, and the mechanical control valve 31 is moved from the internal supply pressure introduction port 43 side.
Further, a predetermined working fluid pressure is supplied to the supply passage 23 on the side of the electric control valve 32.

In this state, while the supply pressure P from the external supply source is equal to or lower than the predetermined pressure, the working fluid pressure by the internal fluid source 40 becomes higher than the supply pressure from the external supply source, and the check valve 51 is closed. Give a valve. Therefore, when the introduction pressure on the external supply pressure introduction port 21 side decreases, the working fluid pressure exceeding the introduction pressure on the external supply pressure introduction port 21 side is increased from the internal supply pressure introduction port 43 side by the mechanical control valve 31 and the electric type. It can be supplied to the supply passage 23 on the control valve 32 side. Therefore, for example, it is not necessary to switch to an operation mode at the time of failure such as a manual steering mode by the mode switching valve 33, but the hydraulic pressure of one system decreases due to leakage or the like,
Even in a state where it is not preferable from the viewpoint of ensuring flight safety, it is possible to ensure the flight safety of the multiplexed actuation system by compensating for a decrease in the external supply pressure of the system.

(Third Embodiment) FIG. 4 is a view showing an actuation system according to a third embodiment of the present invention. The actuation system of the present embodiment is configured to supply the working fluid from the external supply pressure introduction port 21 to the mechanical control valve 31 and the electric control valve 32 and to supply the electric control valve 32
From the mechanical control valve 31 to the external supply pressure introduction port 21.
A check valve 61 for preventing backflow to the side is provided. Here, the check valve 61 opens and closes in accordance with the pressure difference between the front and rear oil passages L5 and L6 which constitute a part of the supply passage 23, so that the upstream oil passage L5 is separated from the downstream oil passage L6. In the case of a high pressure, the valve is opened by a differential pressure between the front and rear oil passages L5 and L6 to form a free flow path, and the flow of the working fluid (pressure oil) from the external supply source to the mechanical control valve 31 in the flow direction Tolerate. Conversely, when the upstream oil passage L6 has a lower pressure than the downstream oil passage L5, the valve is closed by the differential pressure between the front and rear oil passages L5 and L6, and the mechanical control valve 31 is moved from the mechanical control valve 31 to the external supply source. Can be closed to prevent the backflow of the working fluid (pressure oil).

That is, in the present embodiment, only the electric control valve 32 of the mechanical control valve 31 and the electric control valve 32 allows the backflow of the working fluid to the external supply pressure introduction port side. ing.

In the system of this embodiment configured as described above, when the introduction pressure on the side of the external supply pressure introduction port 21 decreases, the working fluid pressure exceeding the introduction pressure on the side of the external supply pressure introduction port 21 is increased. The supply can be supplied to the mechanical control valve 31 from the supply pressure introduction port 43 side. On the other hand, when a large load pressure acts on the electric control valve 32 from the actuator 10 side in the normal FBW control mode, the electric control valve 3
Backflow of the working fluid from 2 to the external supply pressure introduction port 21 side is allowed. Therefore, it is possible to prevent an excessive force from being applied to the body-side structural member 1 which is a support portion of the actuator 10.

(Fourth Embodiment) FIG. 5 is a view showing an actuation system according to a fourth embodiment of the present invention. The actuation system of the present embodiment is provided with a relief valve 71 set at a predetermined discharge pressure in the discharge passage 28 for the working fluid. Also, the relief valve 71
Discharge passage 2 on the upstream side and downstream of the pump 41
A pressure accumulator 72 is connected to 8, and a certain back pressure is applied to the pump 41 by the relief valve 71 and the pressure accumulator 72. In addition, the relief valve 7
1 and the accumulator 72 are each publicly known, and are selected according to the setting conditions of the back pressure.

As described above, in the present embodiment, a constant back pressure can be applied to the pump 41 of the internal fluid source 40 according to the set pressure of the relief valve 71 disposed in the discharge passage 28. Therefore, the required supply pressure can be generated in a timely manner by the pump 41 of the internal fluid source 40 regardless of the operation state of the actuator 10.

(Fifth Embodiment) FIG. 6 is a view showing an actuation system according to a fifth embodiment of the present invention. The actuation system according to the present embodiment is provided in one and the other oil chambers 13 and 14 of the actuator 10.
A mode switching valve 43, which is a 7-port 3-position switching valve, is connected, and the actuator operation mode is switched by switching the mode switching valve 43.

The mode switching valve 43 includes control valves 31 and 3
6 is connected to one of the control pressure ports 31c, 31d or 32c, 32d.
As shown therein, a manual steering mode position connected to a mechanical control valve 31 and an FBW connected to an electric control valve 32 are shown.
It is possible to switch between a control mode position and a bypass mode position in which one and the other oil chambers 13 and 14 of the actuator 10 communicate with each other.

The mode switching valve 43 turns ON / OFF two types of operating pressure switching solenoid valves 45A and 45B.
Switching is performed by increasing or decreasing the pilot pressures Pa1 and Pa2 according to the OFF state.

More specifically, the mode switching valve 43 includes a pair of control valve ports 33a, 33b and 33c, 33d connected to the control pressure ports 31c, 31d and 32c, 32d of the control valves 31, 32, respectively. And the discharge passage 2
8, a pair of actuator-side ports 43 f and 43 g connected to one and the other oil chambers 13 and 14, and a pair of pilot pressure introducing portions 43 h 1 and 43 h 2. Further, the mode switching valve 43 biases the valve body 43j in a direction opposite to the pilot pressure introduction sections 43h1, 43h2, and a valve body 43j that is displaced in accordance with the biasing force from the pilot pressure introduction sections 43h1, 43h2. And a spring 43k.
Any one of the control pressure ports 31c, 31d or 32c, 32d of the mechanical control valve 31 and the electric control valve 32
Can be connected to the oil chambers 13, 14 or can be switched to a bypass mode position.

A solenoid valve 45 for switching the operating pressure is provided.
A and 45B are a valve body 45d and a spring 45e, respectively.
And when the switching control signals Sc1 and Sc2 are respectively input to the electromagnetic drive unit 45f, the respective valve elements 45d are displaced from the OFF position shown in FIG. 6 to the other ON position, Pilot pressures Pa1 and Pa2 are applied to the mode switching valve 43 through the outlet port 45c. That is, the solenoid valve 45
A and 45B are mode switching control signals Sc from the FCC.
1, according to Sc2, the working fluid pressure on either one of the external fluid supply source and the reservoir circuit is set as the pilot pressure Pa as the pilot pressure introducing portion 4 of the mode switching valve 43.
It is a switching operation pressure control means for supplying to 3h1 and 43h2.

In this embodiment, the same effects as those of the above-described embodiment can be expected, and the actuator can be operated in the bypass mode.

In each of the above embodiments, the actuator has been described as an actuator for controlling the control surface of an aircraft.
Needless to say, the invention may be applied to a hydraulic actuator for other uses to be controlled, and the present invention can be widely applied to all FBW-controlled hydraulic actuator systems with a mechanical control mechanism.

[0053]

According to the present invention, the internal fluid source is connected to the supply / discharge passage of the working fluid from the external fluid source to the actuator, and is provided separately from the external supply pressure introduction port for introducing the working fluid from the external fluid source. An internal supply pressure introducing port for introducing a working fluid from an internal fluid source is formed, and the working fluid is supplied to the mechanical control valve and the electric control valve from both the external and internal supply pressure introducing ports. Therefore, when the supply pressure and the supply amount from the external fluid source decrease, the internal fluid source can be operated to compensate for the decrease, and flight safety can be ensured.

[Brief description of the drawings]

FIG. 1 shows an actuation system according to the present invention.
FIG. 1 is a schematic configuration diagram showing one embodiment, showing a state of a manual steering mode by a mechanical control valve.

FIG. 2 shows a second embodiment of the actuation system according to the present invention.
FIG. 1 is a schematic configuration diagram of main parts showing an embodiment.

FIG. 3 is a schematic diagram showing a main part of an actuation system according to a second embodiment of the present invention.

FIG. 4 is a schematic diagram showing a main part of an actuation system according to a third embodiment of the present invention.

FIG. 5 is a schematic diagram showing a main part of an actuation system according to a fourth embodiment of the present invention.

FIG. 6 is a schematic diagram showing a main part of an actuation system according to a fifth embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 Actuator 11 Cylinder 12 Piston 13, 14 Oil chamber 20 Supply / discharge control mechanism 21 External supply pressure introduction port 23 Supply passage (supply / discharge passage) 25 Input link 28 Discharge passage (supply / discharge passage) 29 Discharge port 31 Mechanical control valve 32 Electric control valve 33, 43 Mode switching valve 35, 45A, 45B Solenoid valve (switching operation pressure control means) 40 Internal fluid pressure supply source (Internal fluid source) 41 Pump 42 Motor 43 Mode switching valve 51, 52, 61 Check Valve 71 Relief valve 72 Accumulator

Claims (6)

[Claims] An actuator for forming one and the other fluid chambers on both sides of a piston housed in a cylinder, for moving the piston by supplying and discharging a working fluid to both fluid chambers, and an external fluid source A supply / discharge control mechanism having a control valve for controlling supply and discharge of the working fluid to the one and the other fluid chambers; and a mode switching valve for operating the control valve to switch a control mode of the supply / discharge control mechanism. An actuation system comprising: an internal fluid source that is connected to a supply / discharge passage of a working fluid from the external fluid source to the actuator and supplies a working fluid at a predetermined supply pressure; An internal supply pressure introduction port for introducing a working fluid from the internal fluid source is formed separately from an external supply pressure introduction port for introducing a supply pressure working fluid. And an actuation system for supplying a working fluid to the control valve from the external supply pressure introduction port and the internal supply pressure introduction port. 2. An actuator in which one and the other fluid chambers are formed on both sides of a piston housed in a cylinder, and the piston is moved by supplying and discharging a working fluid to and from the two fluid chambers, and is switched by a mechanical operation input. It has a mechanical control valve that is operated and an electric control valve that is switched by a steering electric signal input, and the supply and discharge of working fluid to and from the one and other fluid chambers is controlled by either of the two control valves. A supply / discharge control mechanism for supplying and discharging a working fluid from a predetermined external fluid source to the actuator, and selecting and inserting any one of the mechanical control valve and the electric control valve into the supply / discharge passage. A mode switching valve for switching a control mode of the supply / discharge control mechanism; and an operating force transmitting member for transmitting an external mechanical operation input to the mechanical control valve. A mechanical control mechanism for operating the mechanical control valve by an operation input via the operation force transmitting member when the mechanical control valve is inserted into the supply / discharge passage of the working fluid to the actuator by the mode switching valve An actuation system comprising: an internal fluid source connected to a supply / discharge passage of a working fluid from the external fluid source to the actuator and supplying a working fluid at a predetermined supply pressure; and An internal supply pressure introduction port for introducing a working fluid from the internal fluid source is formed separately from an external supply pressure introduction port for introducing a working fluid of a predetermined supply pressure, and the external supply pressure introduction port and the internal supply pressure introduction An actuation system, wherein a working fluid is supplied from a port to the mechanical control valve and the electric control valve. 3. The supply of working fluid from the external supply pressure introduction port and the internal supply pressure introduction port to the mechanical control valve and the electric control valve is allowed, while the supply of the working fluid from the mechanical control valve and the electric control valve is allowed. The actuation system according to claim 2, further comprising a check valve for preventing backflow to the external supply pressure introduction port and the internal supply pressure introduction port. 4. A check valve which permits supply of a working fluid from said external supply pressure introduction port to said mechanical control valve, while preventing backflow from said mechanical control valve to said external supply pressure introduction port. 3. The method according to claim 2, wherein a backflow of the working fluid to the external supply pressure introduction port side is allowed only from the electric control valve among the mechanical control valve and the electric control valve. Actuation system. 5. A relief valve set at a predetermined discharge pressure in a discharge passage of the working fluid, wherein the internal fluid source pressurizes the working fluid from the discharge passage of the working fluid to increase the pressure of the predetermined supply pressure. The actuation system according to claim 1, further comprising a pump for supplying a working fluid. 6. A switching operation pressure control means for introducing a working fluid from said external supply pressure introduction port and controlling an operation pressure for switching a control mode of said supply / discharge control mechanism by said mode switching valve is provided. 6. The method according to claim 1, wherein:
The actuation system according to any one of the above.