JPS59175603A - Controlling actuating device - 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 TECHNICAL FIELD The present invention incorporates an electro-mechanically controlled, hydraulically actuated actuator for use in driving a fluid servo system, and more particularly, a main control valve of the servo system. The present invention relates to a flight control servo device for an airplane equipped with a control actuation device.

BACKGROUND OF THE INVENTION Fluid servo systems are used in many applications, such as for positioning flight control surfaces in airplanes.

In such applications, redundancy (reserve) in the device becomes necessary to improve reliability in various operating modes, such as increased control mode or whistle mode, dynamic mode G, etc.

In conventional electro-hydraulic systems, multiple redundant electro-hydraulic valves are used in combination with multiple redundant servo valve actuators, such that any one of the valves and/or actuators
This ensures proper position control of the main control servo valve of the device in the event that one of the main control servo valves fails. Typically, the servo valve actuator acts on the ends of both sides 1 of the linearly movable valve element of the main control valve, and the servo valve actuator is located throughout the device housing.

It is controlled by a pneumatic-hydraulic pressure valve. Although the servovalve actuator(s) can advantageously be able to drive a linearly movable valve element against large reaction forces, such redundancy (having extra reserve force) ) provides many additional electrical and hydraulic components necessary to perform the various detection equalization, timing, and other control functions, thus making the entire device stand-alone. This leads to a reduction in overall hexity, an increase in package size and cost, and requires additional requirements to be placed on the associated electronic circuitry.

An alternative to the electro-hydraulic control system is an electro-mechanical control system that mechanically couples the power motor directly to the main control servo valve. In this device, redundancy can be obtained by mechanical summation of tangential forces in multiple coil powered motors, which is more redundant than summation of hydraulic forces using multiple electro-hydraulic valves and actuators. It is different from ordinary electro-liquid devices that have different characteristics. In the event of a failure of one coil or its associated electronics, the other complementary channels maintain control and the failed channel is disconnected and disabled. However, this method is unable to provide the required force to the main control servo valve within the size and weight limitations that the direct drive power motor at the current stage allows, which necessitates the use of rare earth magnetic materials. There is a practical limit.

In an airplane flight control system, it is convenient and desirable to perform a controlled realignment of the main control→J-bo valve in the event of a total failure or closure of the electric mode. This is desirable in controllers that manually provide input to the main control servovalve, especially when mechanical switching is required after a number of failures have rendered the electric mode inactive. In this known servo device, an electrical input acts on the movable sleeve of the main control servo valve.
Manual input acts on the spool of the main control servo valve.

When the electric mode is deactivated, it becomes necessary to move the valve sleeve to a neutral or centered position and lock or lock the movement of the valve sleeve relative to the valve spool controlled by manual input. Heretofore, this has been accomplished with a centering spring device that moves the valve sleeve to a centered or neutral position and a spring loaded plunger that engages a slot in the valve sleeve to lock movement of the valve sleeve.

The valve plunger is normally maintained disengaged from the slot by pressure of the hydraulic device during operation in the electric mode.
The valve plunger also has a tapered tip that engages a slot in a similarly tapered valve sleeve to facilitate centering of the valve sleeve.

Redundant control actuators are preferred for use in systems where the required stroke of the main control valve element is relatively small and approximately equal to the required stroke of the pilot valve. However, in some cases there are devices in which the required stroke of the main control valve element is relatively long, and within the permissible dimensions and weights, it is several times longer than the stroke of the pilot valve. For example, such a device may be used for flight control.
6.8 to 94.61/min (15 to 25 gal/min) of the main control valve: a speed and approximately ±1.27 s+x (0.05
The pilot valve must have a flow rate of less than 1 gallon per minute and a stroke of ±0.381 ns (0.015 inch) for a main control valve stroke of 1 gallon per minute or more. There are cases.

For long stroke applications, power motors are required to have high output energy capacity. The energy required of a power motor to drive a pilot valve is approximately proportional to the required force and the stroke it must exert, and the level of force is approximately equal to the shear at the tip of a particular valve in an airplane. Generally, it depends on the conditions. In some devices, relatively long stroke conditions are imposed on the pilot valve, which places an energy burden on the power motor. High energy power motors are therefore required, but such motors are undesirable because they are large, heavy, and require high electrical power, power, and associated large electrical circuitry and heat dissipation equipment.

OBJECTS, STRUCTURES AND EFFECTS OF THE INVENTION Accordingly, an object of the present invention is to provide a control actuation device that can be advantageously applied to devices requiring a main control valve with a relatively long stroke. Briefly, the present invention provides an electro-mechanically controlled, hydraulically actuated actuator for driving a main control valve of a servo actuator controller. The actuator has a tandem piston connected to a main control servo valve, and the fll1m1 positioning of the actuator piston is provided by a multi-stage valve using a power motor of relatively short stroke and therefore minimum size and energy capacity. Even though the dimensions and output energy capacity of the motor are relatively small, they are subject to large reaction forces ξI over a relatively long stroke when the valve is actuated hydraulically by one or both of the hydraulic devices. Can drive the main control valve.

In particular, a multi-stage drive valve is provided with a linearly movable tubular valve plunger whose one end is connected to a flexible tile (hollow shaft). A rotary or linear power motor is connected to the protruding portion. In the rotary cap motor, a ball bearing is provided on the tile, and this ball shaft is engaged with an eccentric pin provided on the drive shaft of the power motor. It absorbs the vertical movement of the ball bearing and prevents large lateral loads from being applied to the valve plunger. Additionally, in the case of a linear power motor, the linearly moving drive member is coupled to a flexible tile, the flexibility of the tile absorbs misalignment of the drive member and valve plunger, and a large lateral negative angle is caused by the valve plunger. never join.

Furthermore, the multi-stage valve is provided with a failure control valve sleeve arranged concentrically with respect to the valve plunger G, and when both hydraulic devices are closed or failure, this failure control valve sleeve moves linearly to displace the valve plunger G. When the piston is moved to the neutral position by the centering spring device H1 acting on the main control servo valve, the fluid pressure is transferred from the pressure receiving surfaces of the tandem unit piston in opposite directions to the faulty control valve. A centering speed control orifice in the sleeve discharges to the return side of the hydraulic system. During normal operation, the fault control valve sleeve allows the valve plunger to apply a controlled differential fluid pressure to each piston section of the tandem actuator piston using fluid pressure from one hydraulic source. It can be moved to the desired position. Furthermore, the device pressure is applied to the actuator via a shutoff valve, which shuts off the actuator from the bag pressure when the device is stopped. Fluid pressure is returned from the other sweat-receiving surface of the ME+ device through a flow-limiting orifice to the return side of the ME+ device, allowing the piston to be hydraulically locked during short-term overload.

It is advantageous to use the control actuation device according to the invention to drive the main control valve of a two-way pressure control device, an electro-hydraulic control device and an electro-hydraulic control device.
It does not have the advantage of having both functions of a mechanical control device, but it also has the advantage of being able to offset the disadvantages of both functions individually.

Such control actuators can be electro-mechanically controlled by linear or rotary power motors within permissible size and mold limitations, and can be controlled electro-mechanically by linear or rotary power motors and have a It is particularly suitable for use in applications where it is necessary to drive the main control valve over a long stroke.

EXAMPLE Next, with reference to the drawings, a detailed description of the present invention T;
In detail with reference to the figures, the dual hydraulic servo arrangement 10 is provided with two identical hydraulic servo actuators 12.14, and the two hydraulic servo actuators are connected to a common output device, for example a double cylinder tandem actuator. 16
Connect to.

The actuator 16 is coupled to a control member, for example a flight control element 18 of an airplane. The two servo actuators normally operate simultaneously to control the position of actuator 16 and flight control element 18. However, it is desirable to perform such position control appropriately for each servo actuator independently of each other so that control can be performed even if one of the servo actuators fails or closes. . By kneading, two servo actuators in the entire device provide a surrogate functional characteristic that enhances the safe operation of the flight control.

The two servo actuators shown in FIG. 1 are identical, and therefore identical parts are indicated using the same reference numerals.

The servo actuators 12, 14 each have an inlet 20 for connection to a source of high static pressure fluid (hydraulic bladder #) and a return port 22 for connection to a hydraulic reservoir. Preferably, two It is best to connect the inlet and return ports of the servo actuators to separate and independent hydraulic systems on the airplane, so that even if one hydraulic system fails or closes, the coating will still be 1% functional. Servo actuators connected to the device operate to provide position control.The hydraulic bladders associated with servo actuators 12 and 14 will hereinafter be referred to as the rear hydraulic system and the front hydraulic system, respectively.

In each of the servo actuators 12 , 14 , a passage 24 connects the inlet 2 o to a master control servo valve 26 . Another passage 28 connects the return port 22 to the main control servo valve 26. Each of 7M24 is provided with a check valve 3o.

The main control servo valve 26 is provided with a spool 32 which is longitudinally movable within a sleeve 34 which is longitudinally movable within a housing 86. Valve section 88.40 (Fig.
and each valve portion is associated with a servo actuator 12, 14 and a passageway 24, 28. Appropriate lands, grooves, and passages are provided in each valve portion of the spool and sleeve, so that either the spool or the sleeve obliquely supports the neutral position ff1l and the center position, and the other valve portion 24, 28 of each servo actuator. It is selectively movable to selectively connect to the respective servo actuator passages 42,44.

The passages 42, 44 of each servo actuator 12, 14 connect to a dual cylinder tandem actuator 16, which has a pair of cylinders 46. Passage 42 for each servo actuator.
44 on both sides of the piston 48 of the corresponding cylinder.
-Connect. Cavitation prevention valve 50 as required
．． 52 may be provided in the passageways 42,44. Piston 48 and cylinder 46 are interconnected by connecting rod 54 and link 57 by output rod 56.
is connected to the control element 18 via.

As can be seen from the foregoing, selective relative movement of spool 82 and sleeve 34 causes valve portion 88.4 to
0 simultaneously, one side of each cylinder 46 is connected to a high-rise pressure fluid source, the other side is connected to a fluid return side, and the output rod 56 is connected to the right or left side as viewed in FIG. make a controlled movement. Even if one of the servo actuators 12.14 is closed, the other servo actuator maintains control responsive to selective relative movement of the spool and sleeve.

Due to the relatively moving spool 82 and sleeve 84,
This creates two separate modes of operation for performing position control functions. For example, a spool can be associated with a manual mode while a sleeve can be associated with a control gain mode or an electric mode.

, positioning of the spool in manual mode is done via a direct mechanical linkage to the control elements in the airplane cockpit. As shown in FIG. 1, the spool has a cylindrical socket 58 in which a ball 60 provided at the end of a crank 62 is accommodated. crank 6
2 is connected by suitable mechanical linkages to the controls of the cockpit of the airplane. See US Pat. No. 8,956,971 for details of this type of mechanical linkage.

Normally, manual mode is not used unless a malfunction causes the motor to switch to electric mode or become inoperable. During operation in the electric mode, the spool 82 is held in a neutral or centered position, and the sleeve 84 is operated by the control actuator 7, which will be described by Your Highness.
0 provides controlled movement to provide a position control function.

The control actuator 70 according to the present invention includes an electro-mechanically controlled, hydraulically actuated actuator 72, which is arranged substantially coaxially with the main control servo valve 26, as shown in the lower left of FIG. Arrange and line up. The actuator 72 is provided with a tandem piston (referred to as "actuator histon") 74, and this tandem piston 74 is inserted into the stepped cylinder hole 76 of the housing 36.
axially movably disposed within. The actuator histone 74 is provided with a bait length 80 at its end proximate to the main control servo valve 26, which projects axially within a cylindrical bore 82 in the housing 36, which extends through the sleeve. 34 and a spool 82. The extension 80 is connected to the sleeve 34 by suitable means. A slot 86 is provided in which a spring-load locking plunger 88 is engaged to prevent axial movement of the interconnected actuator piston 74 and sleeve 34, as described in more detail below. Locking plunger 88 is normally maintained disengaged from slot 86 by the H-force of the hydraulic system during operation in the electric mode.

The tandem actuator piston 74 is provided with two serially connected piston portions 90,92. The piston part 90 has a cylinder pressure receiving surface 94 and a source (SOurC; e l pressure receiving surface 96) which is opposite to the cylinder pressure receiving surface.
and has. Similarly, the piston portion 92 and the cylinder pressure receiving surface 98 and this cylinder receiver 11. It has a source pressure receiving surface 100 facing opposite to surface 98 . The cylinder sweat-receiving surface in each piston portion has a larger effective pressure-receiving area than the source pressure-receiving surface. The cylinder pressure-receiving surfaces and the source receivers IllZi1M1 of each piston portion are oriented in opposite directions and have equal effective pressure-receiving areas. As a result, unbalanced forces act on the piston portion, making it impossible to obtain harmonious characteristics.

The source pressure receiving surfaces 96.100 of the piston portions 90.92 are in fluid communication with passageways 102, 104, respectively, and these passageways 102.104 are connected to stop valves 106.
If and T are connected to 108, the shutoff valve 106 and 108 are ordinary solenoid-operated three-way valves, and the supply passage 11 for energizing and positioning is used.
0 and 112 are communicated.

These supply passages 110 and 112 allow the shutoff valve 10
6 and 108, respectively, the servo actuator 14
and 12 to the supply sides of the associated forward and aft hydraulics. When the shut-off valves 106 and 108 are de-energized, they connect the passages 102 and 1(]4, respectively, to the return passages 114, 1 of the hydraulic system.
16, and stiff return passages 114, 116 connect to the return sides of the forward and aft hydraulic systems associated with the thermal exhaust tuator 14.12.

return passages 114 and 116 as described below;
Fidget centering speed control device or control orifice 11
8 and 120 are provided.

Referring also to FIGS. 2 and 3, passages 102 and 104 are also connected to a spaced apart multi-stage pilot valve 125 by passages 122 and 124, respectively. further connecting passageways 122 and 124 to ports 126 and 128, respectively, of fault control valve sleeve 130;
These vents 126 and 128 are in fluid communication with the annular 11ff 182 and vent 184 of the permanently stationary vent sleeve 136. Fault control valve sleeve 130 and tracer sleeve 186 are arranged concentrically within bore 188 of housing 36 , with fault control valve sleeve 180 disposed within housing 86 .
and port sleeve 186, and port sleeve 136 is secured to housing 86 against axial movement.

As shown on the right side of FIG.
2, the end piece 142 axially abuts against a stop plug 144 secured to the housing 86 to prevent axial movement of the sleeve 186 to the right as viewed in FIG. do. The row length 140 is further provided with a diametrical slot through which a diametrically extending pin 146 secured to the housing 86 passes. A ball-shaped portion 148 is provided at the center of this pin 146. This ball-shaped part 1
48 acts as an axial stop, and the plug insert 150 is crimped onto this stop G.

This plug insert 150 is fixed to the wing part 140 by a bottle 152. Thus, as shown, plug insert 150 engages ball-shaped portion 148 of bottle 146, thereby preventing any axial movement of port sleeve 136 to the left as viewed in FIG.

The fault control valve sleeve 180 has a cylindrical outer surface of constant diameter, with a radially inner surface of the fault control valve sleeve 1300 and an opposing sleeve 18 facing the inner surface.
The radially outer surface of 6 is radially stepped along its axial length to provide several valve sleeve sections of different thickness.

As a result, the fault control valve sleeve has a 126°12
8 and a central portion 154 with a slightly reduced thickness between the openings 1 and 1.
Another reduced thickness π-direction portion 15 extending to the left of 26
6, thereby providing a second
2 (differential pressure receiving surfaces 158 and 16 in
yields 0. Therefore, when either or both of the ports 126 and 128 are connected to their respective high HE+ixt sources, the fault control valve sleeve 1'IO
86 to the right and assumes the constraint 1 possible position shown in FIG.

Such movement of the fault control valve sleeve 130 is opposed by a force created by a spring 162, which is located at the right end of the hole 138, with each end of the spring connected to the hole 1.
38 end wall 164 and shoulder 166 of valve sleeve 180
Crimp it. Spring 162 is therefore directed toward vent sleeve 130 in a direction to the left of fault control valve sleeve 180 when viewed in FIG.
toward the radially outwardly projecting flange 168 of.

This flange 168 acts as a stop, and when the fault control valve sleeve abuts this flange 168, it is in the controllable position of the fault control valve sleeve.

The end wall 164, on the other hand, acts as an opposite stop such that the fault control valve sleeve is ready for control when the cylindrical extension 170 of the fault control valve sleeve abuts this end wall 164 as shown in FIG. position.

Failure 4ri? When MI valve sleeve 130 is in the controllable position as shown in FIG.
6 ports 176 and 178 and passages 180 and 182
The kneading passages 180 and 182 communicate with the cylinder pressure receiving surfaces 94 and 9, respectively, as shown in FIG.
Connects to 8.

Additionally, ports 176 and 178 are associated with corresponding axially arranged valve portions of valve plunger 184.

The valve plunger 184 of the multistage pilot valve 125 is
0 sleeve 186 so as to allow only axial movement. The valve portion of the valve plunger associated with the port 176 is defined by annular grooves 186 and 188;
These annular grooves 186 and ]88 are axially separated by adjustment lands 190. Adjustment land 190 is connected to associated vent 17 when valve plunger 184 is in the inactive position.
6 and annular groove 18'6 and 188 are prevented.

However, if the valve plunger moves axially relative to the port sleeve 186 and slips out of the poor crop position 1 IF+,
41 openings 17 by adjusting land 190 based on the direction of movement
6 and the annular groove 186 and the 10,000 or usage of ]88.

The annular p1s 6 is in fluid communication with a port 192 of the port sleeve 136, which port 192 is connected to the fault control valve sleeve 13.
0 is in the controllable position of FIG. 3, it communicates with the vent 126. Therefore, when passageway 122 is brought into contact with supply passageway 110 by stop valve 106, fluid pressure is applied to annular groove ls.
Join 6. At the same time as kneading, fluid pressure is applied to the piston part 9
Source of 0 + El-mountain; also added to 96. The other ring 188 communicates with the opening 194 of the tracer sleeve 1.86;
This port 194 and the port 1 of the fault control valve sleeve 130
Via 96.

It communicates with a passage 198 connected to the *ij return passage 114 downstream of the orifice 118 shown in FIG.

The annular groove 188 is therefore connected to the corresponding or forward hydraulic device σ) on the return side.

Similarly, the valve portion associated with the passage 178 of the valve plunger 184 has a pair of annular i/7200.202 with kneaded annular grooves axially separated by an adjustment land 204, which It functions similarly to the adjustment land 190 associated with the port 176.

An annular groove 200 is in fluid communication with a port 134, and the other annular groove 202 is in fluid communication with a port 206 in the port sleeve.
Through a passage 210 connected to the opening 208 of the valve sleeve 130 and to the s-path 116 downstream of the orifice 120 shown in FIG. 6.

The pilot valve 125 is further provided with a passage 212 which connects the passage 210 to the right-hand or outer end of the bore 138 as viewed in FIG. Therefore, the right end surface of the valve plunger 184 receives pressure from the return side of the rear hydraulic device 6. Furthermore, the pilot valve 125 has a passage 21.
4, which connects the right end of the bore 188 to the left end of the bore 188 so that the left end face of the valve plunger 184 receives the same fluid pressure as the right end face. Further, the effective pressure receiving area of the left end face and the right end face of the valve plunger 184 are made equal, so that even if the pressure on the return side varies, unbalanced force and input are not applied to the valve brush plunger.

Selective axial movement of the valve plunger 184 relative to the vent sleeve 186 provides simultaneous control of both valve sections and provides separate fluid control on oppositely oriented pressure surfaces of each of the piston sections 90t6 and 92. The pressure devices act to apply different fluid pressures. Valve plunger 18
Movement to the right from the inactive position causes fluid pressure to be applied to the cylinder pressure surface 94 of the piston portion 90 from the supply side of the associated forward hydraulic device and from the cylinder pressure surface 98 of the piston portion 92 to the associated rearward hydraulic pressure device. Fluid pressure is released on the return side of the hydraulic arrangement. Due to the pressure imbalance caused by kneading, the unit valve stone 74 and the main control servo valve 2
60) Move the sleeve 84 to the right when looking at it from the 1st position.

Conversely, when the valve plunger 184 is moved leftward from the inactive position, fluid pressure is applied to the cylinder receiving surface 98 of the piston portion 92 from the supply side of the rear hydraulic device, and the forward fluid is applied from the cylinder pressure receiving surface 94 of the piston portion 90 Fluid H/force is released on the return side of the pressure application. In these situations, the resulting pressure imbalance causes the piston 74b to move to the left when looking at the sleeve 34 in FIG. The movement applies different fluid pressures to piston portions 90 and 92, allowing actuator piston 74 to move in both left and right directions. Additionally, the valve portion of the valve plunger associated with one piston portion and the kneading maintains control of the actuator piston even if the pressure relief device associated with the other piston portion and the other valve portion is closed or disabled. I can say that.

To explain with reference to FIG. 3, valve plunger 1
Selective movement of subassembly 84 is accomplished by a power motor 218 located proximate one end of the valve plunger. This power motor 218 is responsive to command signals from the airplane's hook bit and provides control input to the valve plunger. Furthermore, it is preferable that this power motor has double-parallel redundant coils, so that even if the electronic circuit associated with one of the coil masters fails (the nine compensating channels prevent interference). Control is maintained M: In addition, an appropriate fault monitor circuit is provided to detect when and which channel has failed, and to disconnect or disable the failed channel.

The power motor 218 has a housing 220 that is mounted to the housing 36 proximate one end of the valve plunger 184 and has a drive shaft 222 projecting perpendicularly to a plane m that includes the longitudinal axis of the valve plunger. The drive shaft 222 is drivingly connected to the valve plunger by a flexible link member or quill (hollow shaft) 224, and opposite ends of the quill 224 are connected to the valve plunger and the drive shaft, respectively. The valve plunger, shown as tubular, has an axial bore 226 into which a quill 224 is inserted.
through the threaded end 228 of the quill 224.
is connected to the closed end of the valve plunger opposite the power motor side. The opposite end of the quill 224 protrudes from the hole 226 for connection with the drive shaft 222, and a ball bearing 22 is attached to this end.
32 is provided, and this ball bearing 232 is engaged with an eccentric pin 234 provided on the drive shaft. In particular, the eccentric pin fits tightly into the inner race of the ball bearing, and the outer race fits tightly into the lateral hole 236 of the quill 224.

Quill 224 has a cylindrical portion 288 and a flexible reduced diameter portion 240 of reduced diameter. Cylindrical portion 288, threaded end 228 of tile to valve plunger] 84
and tightly fit into the axial hole 226 of the valve plunger such that the deflection of this tile causes the small diameter portion 24
Make it occur only at 0. The flexible small diameter portion 240 absorbs the vertical movement of the bearing 282 and prevents large f and rm loads from being applied to the tubular valve plunger when the eccentric pin 284 is driven over a short arcuate stroke by the power motor 218. It can be done. Additionally, the effective length of the tile can be adjusted at the threaded end 228 to adjust the neutral or inactive position of the valve plunger relative to the inactive position of the power motor.

Valve plunger 184 moves in a straight line! It can also be driven by a vI type (linear) power motor. For this reason, the quill 224
At the connection end with the power motor, an axially threaded hole 244 is provided for connection with the linear drive element of the linear power motor. When using a linear power motor, the flexible tiles allow for such misalignment between the drive member and the valve plunger, and avoid placing large lateral loads on the valve plunger. .

As discussed above, controlled selective movement of valve plunger 184 is provided by power motor 218, which is configured to respond to command signals from, for example, an airplane hook bit.

In order to provide proper feedback information to the command system controlling the power motor, a position transducer 246 is coupled to the end unit piston 74, as shown diagrammatically in FIG. This configuration allows the stroke of the valve plunger and power motor to be relatively short T compared to the stroke of the actuator piston 74. This actuator histone 74 is -4; flx] control valve sleeve 84
A relatively long stroke is required to drive the motor. This reduces the space occupied by the valve plunger, the size and energy storage of the drive motor, and the space required to carry out the fault control functions described below.

This fault control function allows the fault control valve sleeve 130 to
Occurs when moving to the uncontrollable position shown in the figure. Fluid pressure exerted on differential pressure receiving surfaces 158, 160 at ports 182 and 184 of fault control valve sleeve 130 causes spring 16
2 is insufficient to overcome the forces exerted by 2, resulting in an uncontrollable movement of this lever. This occurs when both of the individual hydraulic devices fail at the same time, upon closure of the electric mode by the shutoff valves 106 and 108 after one or more has failed, rendering the electric mode inoperative. In the event of such failure and closure, the spring 16
2 moves the fault control valve sleeve 180 to an out-of-control position where the inner end of the valve sleeve abuts the flange 168 of the vent sleeve 136.

When the fault control valve sleeve 130 is in the out-of-control position,
Between cylinder pressure receiving surfaces 94 and 98 and supply passages 122 and 124 corresponding to kneading? i+1-. is blocked by the fault control function leave regardless of the position of the valve plunger 184. In particular, a faulty control valve sleeve in the out-of-control position will close communication between passageway 122 and port 192. When the fault control valve sleeve is not in this out-of-control position, communication between the passageway 122 and the port 192 can provide fluid pressure to the annulus #186 associated with the cylinder pressure surface 94. Additionally, the out-of-control position of the fault control valve sleeve prevents communication between passage 182 and port 178 associated with cylinder pressure surface 98 .

In addition, when the fault control valve sleeve 130 is in the out-of-control position, the position of the valve plunger 184 is maintained, except for the corresponding centered leak control or metering orifices 250 and 252 provided in the fault control valve sleeve. In particular, N is used to prevent communication between the cylinder pressure receiving surfaces 94 and 98 and the return passages 198 and 210 corresponding to the kneading pressure receiving surfaces.
Fault control valve sleeve 130 moves to the out-of-control position, thereby blocking communication between vents 176 and 172 and opening passageway 18 through metering orifice 250.
0 and passageway 198. Again, communication between passageway 182 and passageway 178 is prevented, and communication between passageway 182 and passageway 210 is prevented from flowing through the metering orifice. 252. As a result, the fault control valve sleeve 13 is removed from the cylinder pressure receiving surfaces 94 and 98.
o to return passages 198 and 210 through aM orifices 250 and 252. The metering orifices 250 and 252 are located on the cylinder receiving face side when the main control servo valve sleeve 84 and actuator piston 74 are moved to the centered or neutral position by the spring centering device 254 for manual mode operation. Control the velocity of the fluid flowing out of it. The spring centering device 254 is shown on the right side of FIG. 1 and can be a conventional spring mounting b'i.

During the operation of the control actuator in electric mode, the shutoff valve 1
Each of 06 and 108 is in the energized state G. This provides fluid pressure from the forward hydraulic system and the aft hydraulic system to source pressure surfaces 96 and 100 of piston portions 9 and 92, respectively. In addition, the aft hydraulic system provides fluid pressure to the end of the spring loaded plunger 256 shown in FIG. As a result, the plunger 25
6 to the right against the spring loading force to open the passageway 258, thereby applying fluid pressure to the locking plunger 88 and forcing it into locking engagement with the sleeve extension 80. Release and main control servo valve sleeve 34
and enables the axial movement of the unitary unit piston 74.

Additionally, body pressure is not supplied to fidget ports 132 and 134 via passages 122 and 124, causing faulty control valve sleeve 180 to move from the uncontrollable position of FIG. 2 to the controllable position of FIG. Moving. With the fault control valve sleeve in this controllable position, the controlled positioning of the unit valve piston 74 and the sleeve 34 of the main control servo valve is controlled by the valve plunger 184 and power in response to electrical command signals from the airplane cockpit. This is done by motor 218. Simultaneous energization of both shutoff valves does not cause large transient changes during energization. That is, the pressure-receiving surfaces of the piston portions are equal, and opposing forces are applied to the pistons due to the above-described pressure-receiving area and opening relationship.

Position control of the unit valve piston 74 and the sleeve a4 of the main control servo valve is maintained even if one of the two systems or channels for the electric mode fails or is inoperable. However, if both σ) channels fail or become inoperative and it is necessary to convert to a manual operating mode, both shutoff valves 106 and 108 are deenergized.

By de-energizing the shut-off valves 106 and 108, the source pressure receiving surfaces 96 and 10 (+) of the piston portions 90 and 92 are connected to the return pressure side and the fault control valve sleeve 130 is
Move to the uncontrollable position shown in the figure. When the sleeve 84 of the main side m servo valve is then pushed towards the center or neutral position by the centering spring device 254, the force of the centering spring causes the now existing pressure and the centering speed control orifice 118, 120 , 250 and 252 force fluid from the actuator mechanism at an uncontrolled rate. Centering speed control orifices 118 and 25 based on the direction in which the centering movement is to be performed.
2, or a centering speed control orifice act simultaneously to control the speed of centering. Providing a control orifice in each piston section ensures centering speed control even if all fluid is lost from one of the hydraulic devices.

Furthermore, centering speed control is performed regardless of the position of the centering unit piston 74 or the position of the valve plunger 184.

When in the manual operating mode, the main control servo valve sleeve 34 is held in a centered or neutral position by the centering spring device 254 and locking plunger 88. That is, when in the neutral position, the locking plunger 8
8 enters the slot 86 of the sleeve extension 80 for locking engagement. If a relatively large reaction force is applied to sleeve 34 that exceeds the holding capacity of the centering spring arrangement and locking plunger, the fluid pressure behind the opposing pressure surfaces of piston portions 90 and 92 will increase. As a result, due to the duration of the reaction force, a relatively large resistance force is generated which acts on the piston and prevents it from being driven backwards. If the time for which a relatively large reaction is applied increases,
When the locking plunger is unseated, fluid is forced out of the centering rate control orifice and eventually the piston moves off center.

What has been described above merely illustrates embodiments of the present invention;
Of course, various changes can be made within the scope of the claims.

[Brief explanation of the drawing]

FIG. 1 is a diagram of a redundant servo envelope comprising a preferred embodiment of a control actuator having a multistage direct drive valve performing a fault control function according to the present invention; FIG. FIG. 8 is an enlarged longitudinal sectional view similar to FIG. 2 of the multi-stage surface driven valve in the actuated state. 10...Double hydraulic servo device 12, 14...Hydraulic servo actuator 16...
Tandem type actuator (output device) 18... Flight control element (control member) 20, °° inlet
22... Return exit 26... Main control? MJ servo valve 32... Spool 84 of the main control servo valve... Sleeve 36 of the main control servo valve... Housing 7o... Control actuation device 72... Actuator of the control actuation device? 4...Tandem type actuator piston 76...Cylinder hole, 80...Extension part of unitary piston...
Spring-loaded locking plungers 90, 92... Piston portions of tandem actuator pistons 94, 98... Cylinder pressure receiving surfaces 96, 100... Source pressure receiving surfaces 106, 108... Closing valves 110, 112... Hydraulic device supply passages 114, 11
6... Hydraulic device return passage 118, 120... Centering speed control bag @ (metering orifice) 125... Multi-stage pilot valve IJO... Failure control valve sleeve 186... Vent sleep 158 .160...Differential pressure receiving surface 184...Valve plunger 218...Power motor 224...Quill 232...Ball bearing 234...Eccentric bottle 246...Position converter 250, 252... - Metering orifice 254...Spring centering device 256...Spring loaded plunger.

Claims (1)

[Scope of Claims] 1. A control actuating device used in a dual micro-pressure servo control arrangement for operating a control valve element having a relatively long travel stroke, comprising an actuator and an axially a tandem unit tabiston movable and drivingly connected to the control valve element; a multi-stage valve means connected to the actuator for moving the unit unit tabiston in both axial directions; The multi-stage valve means is driven linearly over a short stroke compared to the stroke of ! A control input means having a power motor means for controlling the position of the actuator piston described in 1j and iIJ is provided, and two piston parts connected in series are provided to the front F actuator piston, and each piston part has an axis line. The multi-stage valve means is provided with a valve plunger having two valve parts connected in series, and the valve plunger is directly driven in both axial directions. The pressure-receiving surfaces of each piston part of the unitary piston are arranged so that the actuator piston moves in both axial directions. A control actuating device characterized in that the multi-stage valve means is configured to perform control to apply different fluid pressures from hydraulic pressure sources corresponding to λ. The control actuation device according to claim 1, characterized in that the control actuation device has a direction opposite to the corresponding receiving pressure TB1. & Supplying fluid pressure to the actuator and the multi-stage valve means from the corresponding hydraulic pressure supply source. A control actuating device according to claim 2, characterized in that a closing means is provided for shutting off the device from the hydraulic pressure supply source. a metering orifice for discharging fluid pressure acting on mutually opposed pressure receiving surfaces of the piston portion in response to closure of the device, and centering means to place the unitary piston in a neutral position. 11. The control operation g position according to claim 10, further comprising a device closing response means for controlling the moving speed. 6. The control actuation device according to claim 4, characterized in that the failure control valve member and the valve plunger are arranged concentrically within the multi-stage valve means. 6. The control actuating device according to claim 5, wherein the symbol is "cow". 7. The control actuation device according to claim 2, wherein the opposing pressure receiving surfaces of both piston portions have equal effective pressure receiving areas. 8 The mutually opposite pressure receiving surfaces of each piston part shall have different effective pressure receiving areas, and means is provided to apply fluid pressure from the i-pressure supply source only to the pressure receiving surface of each piston part which normally has a smaller area, When the valve plunger moves, the valve portion of the valve plunger acts to apply fluid pressure from the hydraulic pressure source to the larger pressure receiving surface of the corresponding piston portion, or the surface phase of the corresponding piston portion is Claims characterized in that the fluid pressure applied to the larger pressure receiving surface is released to the return side to the supply source, and the actuator piston is moved by the fluid in both axial directions. 1. Control operating device for the inspector. 9 The pressure-receiving surface with the smaller area and the pressure-receiving surface with the larger area of each piston part are oriented in opposite directions with respect to the axial direction, and have an equal effect on the corresponding pressure-receiving surface of the other piston part. 9. The control actuation device according to claim 8, characterized in that it has: ]0 A fault control valve member movable in the axial direction within the multistage valve means; and a failure control valve member that is movable in the axial direction within the multistage valve means; and a failure control valve member moving means for moving the failure control valve member from an uncontrollable position that prevents the application and release of fluid pressure to the pressure receiving surface with a larger area to a controllable position that allows this application and release. Claim 1 (8) A control actuating device according to claim 1 (8). 11. A closure for releasing the fluid pressure acting on the pressure receiving surface of the smaller area of each piston portion to the return side of the hydraulic pressure supply source. means for resiliently urging the actuator piston to a neutral position when said closing means is actuated; and said failure control valve when said closing means is actuated to cause a release of fluid pressure. 11. The control actuating device according to claim 10, further comprising a suppressing means for pressing the member to the uncontrollable position.12. The total liquid pressure from the pressure-receiving surface of the piston part with a larger ml lL+ is configured to have a vent means on the return side of the source through a corresponding centering speed @1 @J orifice. 12. A control actuator according to claim 11, characterized in that the actuator means is configured to control the speed at which the front Jf' centering means moves to the neutral position.18. Claim 12, characterized in that it is arranged on a failure control valve member.
Control actuation device as described. 14. The control actuation device according to claim 12, wherein the failure control valve member and the valve plunger are arranged concentrically with a multi-stage valve means. 15. The control actuation device according to claim 14, wherein the failure control valve member is a sleeve surrounding the valve plunger. 16 The fault control valve member moving means moves the two differential pressure receivers previously formed on the fault control valve member, and the g-plane of these two differential pressure receivers, to the one having a smaller facet of the piston portion. S by means of communicating with the pressure applied to the pressure receiving surface of
The control actuation device Wt according to claim 10, characterized in that: 17. The control operation according to claim 8, wherein the valve plunger has opposite end faces having equal effective pressure receiving areas, and is provided with pressure applying means for applying equal fluid pressure to these end faces. Device. 18. The N control actuation device according to claim 17, wherein the pressure applying means described in 9-ij is a communication means for fluidly communicating the end face with the return side of one of the hydraulic pressure supply sources. 19. The control actuation device according to claim 1, wherein the valve plunger has mutually opposite end faces having equal effective pressure receiving areas, and is provided with pressure applying means for applying equal fluid pressure to the stiff end faces. . 20 A control actuation device for use in a hydraulic servo actuator control device for operating a control valve element, comprising an actuator and a unitary piston movable in the axial direction within the actuator and drivingly connected to the control valve element. and a multistage valve plunger connectable to a control input means for controlling the position of the actuator piston and capable of direct expansion and movement for directing fluid pressure toward the actuator piston to move the unit piston in the axial direction. valve means, centering means for biasing said actuator piston to a neutral position when said control input means is deactivated, and centering means on opposite sides of said actuator piston responsive to deactivation of said control input means. a discharge means for discharging fluid pressure acting on a side surface through a metering orifice to control the rate at which the centering unit is forced into a neutral position; is provided with a failure control valve member linearly movable within the multi-stage valve means to a position capable of releasing fluid pressure from one side of the unitary piston by connecting the corresponding metering orifice; A control actuation device characterized by: 21. The control actuator of claim 20, wherein each 2L metering orifice serves as said fault control valve member. 22. The control actuating device according to claim 20, wherein the control valve member and the valve plunger are arranged concentrically with the multi-stage valve means. 28. Claim 2, wherein the failure control valve member is a sleeve surrounding the valve plunger.
2. Comparison of control actuation devices. 24 One side surface of the flat unit tabiston has a larger pressure-receiving area than the other side surface, and a normal pressure applying means is provided for applying fluid pressure only to the pressure-receiving surface with the smaller area of the flat unit tabiston, A patent claim characterized in that the valve plunger is selectively movable so as to apply or release fluid pressure to a pressure-receiving surface with a larger area in order to perform a bidirectional movement operation in the axial direction of the actuator piston due to pressure. 21. The control actuation device according to claim 20. 21L The discharge means prevents normal fluid pressure from being applied to the pressure-receiving surface with the smaller surface area in response to the input control means being inactivated, and prevents the fluid from being applied to the pressure-receiving surface with the smaller surface area. 25. A control actuation device according to claim 24, further comprising valve means for discharging pressure from the other metering orifice. 2e - Preventing the application and release of fluid pressure to the smaller pressure receiving surface when the fault control valve member is in the position for discharging fluid pressure; 26. Control actuation device according to claim 25, characterized in that it allows dosing and dispensing. 1. An elastic pressing means for elastically pressing the failure control valve member to the position; 27. The control actuation device according to claim 26, further comprising a moving means for moving the control valve member to the position of the piston. 28. The moving means has pressure receiving surfaces formed on the failure control valve member that have mutually different effective pressure receiving areas and facing in opposite directions, and these pressure receiving surfaces are in fluid communication with the normal pressure applying means. Control actuation device FF according to range 27.