DE1809344A1 - Pressurized drive - Google Patents

Description

"Pressure fluid operated drive"

The invention relates to a pressure medium-actuated drive a power transmission part and a control part, in the pressure medium is fed under pressure, with a flow regulator to determine the operating speed. Subject of the invention is an auxiliary control system with the special purpose, as a new type of control device for the flight operations with wire "(" fly-by ~ wire "), the duplicated or surplus units contains. The term "wired operations" can be used as A constructive version of the conventional IPlug operation be considered, in which the forces are transmitted with control cables, which are from the control stick of the pilot to the Guide control surfaces or the control surface actuators. In plug operation with wire, such ropes and signals are not required are transmitted directly from the joystick or another signal source to a motor that is the actuating device for the control surface represents. Conventional, mechanical, primary control systems that the pilot uses by means of his control wheel and operated the control surface of an aircraft by means of ropes or operated the main actuator for the control surface a limit to the development by the provisions for the

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~ ² ~ · 18 093A4

Restriction on the use of mechanical elements 'found in such a system' With such primary tax. er systems there are mechanical elements with play between the adjustable parts, which means a lack of simultaneity and similarly a discrepancy between the movement of the steering wheel and the operation of the surface "means. But besides dead play there are other restrictions on the use of systems with mechanical elements. ■ ■ ": -,

To the extent that the primary tax system is complex is multiplied to meet the growing sharp demands too that are imposed by the high perfection and variable geometry of an aircraft also increases the sensitivity of the system to errors the entertainment and the safety and reliability decreases.

Since a system with mechanical linkage is always a single-channel system with a considerable cross-section, which is due to the arrangement of the operating elements ₃ , it is highly sensitive to injuries in combat.

One can see the disadvantages of conventional mechanical control rods, for controlling aircraft surfaces using electrical and electronic techniques. The I non-uniformities The operation of mechanical linkages is eliminated by using the primary stick control system electro-hydraulically mechanized, and one arrives at an increased Perfection, but there is an electronic or hydraulic one Element is even lighter than a comparable mechanical one Part, one applies multiple channels, also known as Surplus channels for the electro-hydraulic systems to »Die Use of carefully isolated redundant channels increases usefulness many times over and if there is a failure takes place in one or more of the channels, it remains one

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Possibility of satisfactory system function remaining. Man thus receives your system with the redundant automatic]? higher reliability and safety together with an improved design compared to those described above Types of primary tax systems.

The object of the invention is the procurement of an improved drive with redundancy channels with low demands on cross channel monitoring. The invention consists in a motor for setting the control member from a normal position to M two mutually associated channels or connections, in a resilient return, actuated by the power transmission part for the purpose of changing the setting or for the purpose of resetting the control member in the normal position or in the normal state and in a regulator for the channels, which determines the duration of the pressurization of the power transmission part and thus the flow of the pressure medium to the power transmission parts. What is achieved by this arrangement is that a channel is switched off in the event of failure and that the remaining channels continue to operate without the performance dropping significantly.

Exemplary embodiments of the invention are shown in the drawing. They are: (|

1 shows a block diagram of a four-channel redundancy control apparatus,

2 shows pressure equalization and shutdown monitoring, shown schematically,

3 shows a block diagram of a redundancy channel together with the summing element for the other four channels,

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4- the block diagram of a second embodiment a jet pipe pressure compensation arrangement and the control for the failure of the monitoring ,

• *

Figure 5 shows the subject matter disclosed in Pig. 4 is included, shown schematically, and

6 shows the schematic representation of a modified form of a detail from FIG. 5 ""

The device has four identical channels for receiving the same control signals and each of them contains an auxiliary motor for suiämes Hydraulic forces. The auxiliary motors can be fed from separate pressure medium sources, it can also be one there must be a smaller number of pressure medium sources than auxiliary engines, Appropriate, pressure-actuated switches are provided for the individual pressure medium source, which is a failed one Switch off the source from the summation and instead connect an undamaged source to the auxiliary motor. The four Auxiliary motors are used to; ,, to drive a common actuator, and each auxiliary engine is directly powered by the Actuation of a part driven from one of the redundancy channels. Adding together a variety of Powers decreases the response of the output member to the failure of a channel and thus allows a simple failure indicator to have a switches off the failed channel.

A simple pressure equalization device for a hydraulic auxiliary motor used to prevent a malfunction is reduced due to incorrect connection of an input or due to inaccuracies within the auxiliary motor.

Requirements for the response to the failure indicator of an auxiliary

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power engine are not so focused when force-summing Auxiliary engines (auxiliary engines with total displacement) are present because the slowness and even the Failure of the display, on which an over he controls the auxiliary motor is switched off, for example, only in a minor way Movement of the output link results.

A jet pipe valve is installed in each channel using a Electrically adjustable diaphragm used, with which proportional control is guaranteed and with which hydraulic oontamination effects that sometimes occur with other arrangements.

A simple hydraulic pressure sensor piston monitors the pressure difference with each individual auxiliary motor piston and sends a time-integrated and limited signal to the rotary motor back, which is the auxiliary force differential pressure and thus the channel mismatch is reduced. The primary provision for the rotary motor linkage, which adjusts the nozzle, comes from the common summing element of the multiple forces, which is adjusted by the four hedundance auxiliary power cylinders will.

The hedundance tax system according to I ¹ ig-. 1 includes a plurality of hedundancy channels A, B, G and D. The channels are similar and one of them will be described. In channel A, an electrically variable signal source, for example a control force converter 17, which is actuated with the movement of a member such as the control stick of an aircraft, in each case sends the control signal to a demodulator amplifier 19j, which in turn sends a control signal through a standard network 20 the summing device 21 outputs. This also receives a control signal from the stabilization and control amplifier system (not shown) through

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the conductor 22. The signal from the summing device 21 is transmitted by a conductor 23 to an auxiliary power amplifier 25 »The output from the amplifier 25 reversibly controls the actuation of a conventional rotary motor 26 _S which via a transmission 27 causes the actuation of a movable member that is differentially Pressure medium supplies the ends of a piston of an auxiliary motor 38. Under the action of the pressure medium, the piston with the piston rod 61 controls a slide 40 common to the four channels, which with its output 41 operates the control valve for the main actuation of a control surface.

The movement of the auxiliary piston and its piston rod 61 on the force summing member 40 is at the same time transmitted to a restoring device of a force-transmitting type for a force summing device within the auxiliary power booster 38. The output from the force summing device is communicated to the auxiliary force control element. The force summing device within the auxiliary force amplifier 38 also receives an input via ¹ a force transmission device 48 from a pressure equalization system 49.

The pressure compensation systems 49 and a monitor are received as input 5Ί the Drutek over the modulating piston in the auxiliary motor 38.

The auxiliary power motor 38 for a channel for totalized hydraulic fluid Fig. 2 shows ". Sr consists of a rotary motor 26 (which receives the variable force converter signal) with a working lever 5Ή which can be varied via a linkage 59 Jet pipe 52 adjusted. A hydraulic fluid is added to the jet pipe by means of a solenoid valve 50 and a line 51 supplied from a pressure medium source P. The outlet 53 starts from the outlet of the jet pipe 52. The jet pipe 52 are two bores or connections 57 »58 assigned, which are in the starting position equal liquid pressure distribution from the jet pipe 52 received. The two connections 57, 58 are connected to the two end faces of a 1 / iodulating col-

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bens 60 in connection. Depending on the force transducer signal, the jet pipe 52 is adjusted by the action of the working lever 54 and its linkage 59 in both directions and causes the reversible movement of the modulator piston 60.The piston rod 61 of the modulator piston 60 is attached to a modulator piston summing element 65 connected, which is used to adjust a control valve for a main engine, not shown. The jet pipe 52 is returned to its starting position by a resetting device which consists of the summing member 63 with the common member 40, a reset spring 64- and a member 65 which is attached to the working lever ^ M- . The element 63 actuated by the hedundancy auxiliary power motors thus controls the resetting of the jet 52.

A hydraulic working cylinder with a piston 67, on the Both end faces the pressure medium acts, is used as a supervisor. It gets through suitable orifices 62 or throttles, which are located in lifting lines that are connected to the main lines on both sides of the modulator !:; lbens 60 are, on the piston 67 · Through the orifices, the action of the piston 67 is based on the previous displacement of the modulator piston 60 delayed. The movement of the monitor piston 67 is transmitted to the working lever 54 of the rotary motor via the return spring 69 (thus by a force member or force-acted return member) and sets the jet pipe 52 back, reducing the pressure from the jet pipe 52 into the connections 57j 53 is made the same.

If a special monitor can also be provided, the hydraulic working cylinder monitor can also be used with the Piston 67 switch a limit switch 72 through a corresponding connection to supply current to a solenoid valve 50 give *?., thanks to suitable Littel, for example a spring closes and the flow of the pressure medium to the one

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adjustable jet pipe 52 interrupts, which indicates that the associated channel has failed.

Figure 3 provides an analysis block diagram of the force summing Auxiliary motor according to Fig. 2, according to which the electric rotary motor sends a signal of variable voltage via a line from the amplifier 25 (Fig. 1). As a converter, the rotary motor transforms the electrical input into a mechanical torque that is proportional to the size of the electrical input. By means of the lever 54 and the member 59 puts it at the beginning of the jet pipe 52 in a Distance that corresponds to the difference between the output of the rotary motor and the force of the two return springs 64 and 69, is tional.

Due to the adjustment, the jet pipe 52 converts the liquid pressure, which is received by ports 57 and 58, proportional to its adjustment, and the modulating piston 60 is adjusted at a speed corresponding to the flow, which results from the pressure difference on both sides. The path of the piston 60 corresponds to the integral of the duration of the Differential pressure and the resulting ■ flow and with the rod 61 adjusts the modulating piston the summing member 63 and the member 40 which acts on the return spring 64, so that a restoring force corresponding to the adjustment of the summing element 63 arises from its starting position. The force that is on the spring 64 acts changes the normal size or the shortest distance between its initial and its initial position. This Force is transmitted from the link 65 to the point 66, where the forces are summed, i.e. on the far end of the working lever 54.

This describes the auxiliary power cycle, but also a second one Circle consists in which the jet pipe 52 through the pressure-sensitive Monitor piston 6? is reset. The difference the pressures on the surfaces of the modulator piston 60, which is caused by any application of the modulator piston to the Hrund Mismatch with other modulator pistons ,, .that with the same

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Chen summing member 40 cooperate, arises and through suitable filters or diaphragms on the pressure-sensitive 'monitor piston 67 », the total displacement or movement of which depends on the sum of the. Differential pressures over the entire time depends on the both end faces of the piston 67 rest. The adjustment will by a spring 69 in the specific pressure during the adjustment of the piston 6? transformed and also to act on the Point 66 brought to the summation of the forces.

In the embodiment of Figo 2, the adjustment of the monitor piston 67 is also transferred to an off switch 72 for M the shutdown process, which is so active that the circuit of the solenoid valve 50 is interrupted and thereby the flow of the fluid from the pressure medium source P to the The switch 72 also controls the power of an indicator to notify the pilot that a channel has failed.

In Figo 3 it is shown that the Moduli he piston X ~, - ^ x ^{urL <} l ^ 4 of the three other Jtiedundanz-auxiliary power motors are connected to the summing element 40. It goes without saying that the rotary motor of each channel is equipped with the same reset devices as

this is the case with channel A. Λ

Even if a mechanical reset for exerting rotational forces by means of loading have been described for the jet pipe 52, there is also the possibility that the settings from the summing element 40 and the pressure-sensitive piston 67 could also be electrical signals that instead of the mechanical resets on the working lever 54 can be brought to the auxiliary booster 25 to the application ₀ in a second embodiment, starting from Fig. 3, that of the arrangement is similar to Fig. 4 with the exception of the fact that the differential pressure acting on the Modulierkolben 60, not only on the monitor (pressure equalizer) 67, for which the modulating piston is brought into action, but also for the

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• Effect is brought to the valve actuation circuit, for which purpose the switch 72 has a special pressure-responsive working cylinder. The reference numbers in FIG. 4 correspond to those ⁷ -in- FIG. 3. ■■ '. ■■; ■ '- ■ ^; "'■ ■ ''^:;:

Except that operated by the pressure of the modulating piston. Switch 72 for the solenoid valve 50 this is also used by others Controlled monitoring circuits. Therefore, Fig. 4 frased on logic relationships, which are explained in the following.

In Fig. 5 you can see a force-summing servo device with the " mechanical! reset according to Fig. 4, shown particularly precisely ο Corresponding reference numbers are the same as 'in' ■ Fig. 2.

Since in Fig. 5, apart from what has been described so far, only other electrical circuits are introduced is execution immediately described by their mode of action. By instantly closing a manually operated "Supervisor switch s 80 (top left) turns the circuit off a DC voltage source (not shown) via the line 81, the switch 80, the conductor 82, the conductor 83, the Magnetic switch 84, the conductor 85, which is closed at the moment, through the winding 86 of a sliding magnet and the conductor 87 closed back to the power source. Before pressing the Switch 80, the solenoid valve 50 is closed and . The pressure from the source P cannot act on the jet pipe 52 get »compartment closing the switch 80 and when the Turn 86 is energized, the valve moves to the right and lets the pressure medium reach the jet pipe 52 at the same time Open the circuit through the switch 84 by means of an extension piece on the valve.

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The switch 72 for switching off the pressure monitor exists of four movable towards each other, fixed with their ends Contacts, two of which 90,91 with extensions on shoulders of movable plunchers 93 »94 on the modulating piston attack the supervisor. Each pluncher 93 * 9 * 1 is made of Return springs 95 * 97 acted upon in the direction of each other. It results that when pressure medium, which flows through the corresponding lines, on the one surface of the pluncher 93s 94 and the normal pressure in the connections 57j 58, which is transmitted by the lines, compresses the return springs 95 »97, actuating the inner switching elements 90, 91 in this way that they touch each other. The outer contacts 98, 99 are normally on the corresponding inner contacts 90.91 on.

With the action on the switch 72 and the closing of its contacts when the solenoid valve 50 opens a hold circuit for the solenoid valve from the DC power source here, over the conductor 88, the closed switch 104, the outer contact 99, the contacts 91, 90, 98, the conductor 100, the conductor 101, the holding winding 102, the tension angle 86 and conductor 87 back to the DC power source. The actuation of the switch 72 for the pressure regulator proceeds as follows themselves. In the event of malfunction due to failure in the signal actuated Amplifier 25 of channel 11, for example, but normal functioning of the other channels, happens in the channel 11 a movement by the force of the summing member 40 and the Piston rod 6l of the piston 60, which the return leaf spring 64 of the cylinder and displaced the jet pipe 52 to which no rotating force is exerted by the rotary motor 26, like this the adjustment of the output member 40 or the summing member 63 corresponds. The unrestricted adjustment of the tube 52 has a large pressure in one or the other of the ports 57,58

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as a result, which is 80 % of the total pressure P and results in a large displacement, for example of the pluncher 9 ^ relative to the pluncher 93 or vice versa, which act on the contact arm 90 and thus the circuit between the outer contact 98 and the inner contact 90 open, wherein the pluncher 93 is active between the outer contact 99 and the inner contact 91 and thereby opens the circuit between the lines 88 and 100, whereby the windings 102 and 86 of the magnet close the valve 50. The closing movement of the valve can be supported with an auxiliary spring 89 which is assigned to the pressure from the hydraulic power source.

In FIG. 5, too, the spring-assisted modulating piston of the pressure compensator 67 is acted upon by a liquid from an orifice 62, so that the flow is limited so that it works over a long-term interval. In the event, for example, that the modulating piston 60 becomes stuck to the A channel and cannot be moved, a differential pressure is built up on the two ends of the modulating piston 60 over an extended period of time when the pressure equalizing piston 67 is operative. The equalizing piston 67 is adjusted because of the presence of a pressure difference over a longer period of time and, by its spring 69, returns the jet pipe 52 to its normal position, where it is the same. Pressure on the two connections 57 ₃ 58 and thus on both ends of the modulating piston.

The circuit between the conductor 88 and the outer contact 99 of the switch 72 includes, as previously described, one of Hand-operated switch 104 so that the channel can also be switched off manually. The switch is then connected quick operation of switch 80, with which the magnet

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valve 50 held in the open or engaged position will be closed.

With regard to the logic quirks of the Pig. 4 is in Fig. The pressure line, which leads to one end of the pluncher 53 of the pressure monitoring switch at its end remote from the support, designated with c _o and the line that brings the pressure on the pluncher 9 ^ with c .. Furthermore the line with the pressure from the source for the pressure pipe 50 is designated by P. 4 shows the system in the event of a shutdown. In other words, the electrical circuit for actuating the valve 50 is open at the contacts 90, 91 when c, + c _{o are} below 0.5 P. The circuit between the contacts 90,98 of the switch 72 is also open when c. - C _{2 is} greater than 0.8 P. Finally, if c ~ - c ^ is greater than 0.8 P_, the switch-on circuit is _{open at contacts 9I 5} 99; or, in the first case, the inner contacts 90, 91 are out of engagement or are not closed. In the second case, the outer contact 98 and the inner contact 90 are disengaged. In the third case or in the third logical switching state (statement), the outer contact 99 and the contact 91 are disengaged. Thus, when the valve 50 is actuated, the magnet winding is not energized when a very low pressure reaches the modulating piston 60 from the jet pipe 52. If the pressure on one side of the modulating piston, measured against the pressure on the other side, becomes very high, the contacts 98, 90 or 99 ₃ 91 separate from one another. As a modification, FIG. 6 shows a pressure equalizer 110 as a cylinder and piston, in which the cylinder contains the piston 6j in a subsection 111 of small diameter and perforated disks 117, HS in the subsections 112, 113 at the two ends. The subsections 112, 113 are connected to the lines c., Cp (Fig. 5) and the subsection 113 contains a throttle in its feed line

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Screen 62. The disk 117 in the sub-chamber 112 rests against one end there and is supported by a pretensioned spring 119. The same applies to the sub-chamber 113 with the disk 118 and the spring 120. There is in the lines c. and C ₀ no pressure, then the disks 117 and 118 exert no force on the piston 67. If, however, there is a differential pressure on the lines c 1, C ₂ , then the force of one of the pretensioned springs 119, 120 is overcome before a force is communicated to the piston I67 for the purpose of moving the jet pipe 52.

The arrangement according to FIG. 6 has its advantages over that according to FIG. 5 ₅ when low static forces or low constant static loads act on the Suminier member 40. For example, the device including the summing member 40 is connected to the main controls such as the joystick and control feel system in an aircraft, and static loads from the control feel system can be applied to the member 40 for steady operation apply static pressure. When using the arrangement according to FIG. 6, a movement of the pressure compensation piston 67 only occurs when the static load exceeds the force of one of the two pretensioned springs 119 and 120. Thus, through the use of springs 115 and 120 in the device according to FIG. Static loads are thus ignored.

The mode of operation is such that each auxiliary power booster, for example, the booster 25 in channel A, the auxiliary power engines is assigned for summed fluid forces, contains a similar electrical control signal. The numerous

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Chen modulating pistons are usually connected to one another Summing member 63 connected. According to the common control signals, the modulating pistons normally have or ideally the same way of working. In reality, however, when this mechanical arrangement is made, it is Nullwat for each of the auxiliary units different because of the Manufacturing tolerances, differences in material, etc. To compensate for these effects and to compensate for the load-bearing capacity of the individual modulating piston is a differential pressure sensing pressure equalizer with the associated Output cylinder connected, on whose modulating piston the differential pressure acts. Since only long-term pressure changes When this pressure modulating piston pressure equalizer is to be effective, the flow is on its opposite side Front sides restricted with the help of panels. The limitation - plus the effect of the adjustment characteristics of the pressure sensor - allows that the input signal to the jet pipe can be modified so that the loads that applied to all modulating flasks, balanced or approximately balanced.

If the failure of only one of the redundancy units occurs, for example a hardover failure due to the failure of the resetting of the auxiliary power - then the pressure sensor (failure switch) moves. this: ¹ "unit because of the high pressure caused by the adjustment of the jet pipe 52 in the direction of one of its outer positions to 80 % of the available pressure P from the pressure medium source, then only the failed coding piston or its auxiliary power unit reaches this pressure level and therefore its failure switch switches

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72, which indicates the failure and prevents liquid from flowing to the associated jet pipe. The ones left over Channels continue their activity.

This Arbeitswese requires that the modulating piston no or have little work to do, as has already been said. This is achieved by moving from the modulating piston a conventional control valve for a main engine beddanen leaves. If some dynamic loads are reflected on the modulating piston, the effect of the line orifices of the pressure sensor (pressure equalizer) reduces this effect.

Failures due to both underdrive and overdrive are detected directly by the failure switch 72. Total failures show up thanks to the utilization of the relatively high Pressure gain, which, when a command is given to the working auxiliary motor, the dead auxiliary motor as appear overdriven in the opposite direction.

The channels may have their own pressure medium sources and their jet pipes must have at least one pressure medium source be engaged by pressure-sensitive switching and remain in it, in the event that the original pressure medium source fails. It goes without saying that the gain in the redundancy channels is measured in such a way that when the overall system calls for the activity of a pressure equalizer supervisor (such as 67 in Fig. 5), the probability is low that the disconnector 72 will respond to such a call.

Calculate the total auxiliary power with hydraulic modulating piston pressure one arrives at one completely

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new instant monitoring of the effectiveness of the channels. If a channel reaches a fault gate of a certain size, then according to the explanation this is synonymous with the failure of this channel, and a switch is actuated. It is essential that this method of monitoring compare the power assist to the average output of all power assistants in that line. This means that you don't need a complicated logical setup if you want to sort out the failed channel. The four-channel system described here is still operationally reliable ₃ even if two channels fail and are switched off, because if a malfunction occurs in one of the channels ₉ the tendency of the output element 40 to perform incorrectly from the remaining, properly working channels is compensated.

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Claims (1)

18 claims 1. Pressure medium-operated drive with a power transmission part and a control part, in the pressure medium, under pressure is fed in and with a flow controller to determine the operating speed g e ke η η ζ e i c h n. e -t by a motor (26) for the position of the control member (67) from a normal position opposite two associated pressure medium channels or connections, actuated by a resilient return (64,65,69) from the power transmission part to change the setting or to return the control member to the normal position or to the normal state and by a Regulator (62) for the channels (57 _} 58), which determines the duration of the application of pressure to the force transmission part (60,61,63) and thus the flow of the pressure medium to the force transmission part. 2. Drive according to claim 1, characterized in that a diaphragm or throttle (62) controls the flow rate determined by determining the position of the control member (67). 3. Drive according to claim 2, characterized by a provision (64 ₃ 65) for the adjustable control member (67) and for the application of the channels with the aid of a flexible and pressurized connection. 4. Drive according to claim 1, characterized by a pressurized monitor (67), the the point (66) of the output of the force with respect to its 909828/1078 ORIGINAL BATHROOM 18Ü93U Position to the input of the force as a puncture of the initiated Force internal size changes and thereby that the monitor (67) is connected to the reset device (64, 65) is and thus with a jet pipe (52) which is displaceable with respect to the position of the channels (57, 58) is. Drive with a main motor and with a control valve for the drive according to Claims 1 to 4, characterized by a multiplicity of redundancy _{channels (A 9} B ₅ C ₃ D) and a pressure-medium-operated auxiliary motor (60) assigned to each channel, which is connected to a summing element (63 ), which is connected to the main control valve, through a wide adjustable jet pipe (52) to generate a Differen2, pressure applied to the redundancy auxiliary motors (60) and through a reset device (64,65) between the summing element (63) and the jet pipe (52) on all redundancy auxiliary craft motors (60). Drive with a power transmission part and a control part that allocates the printing means and for this purpose has a Modulierkolben which determines the Steuerungsgeschwhdigkeit and thus the adjustment value of the force transmitting member, characterized by at a jet pipe (52) with which a monitor is moved (67) from its normal position , by a resetting device (64,65) between the power transmission part and the monitor piston for the purpose of returning it to the starting position through pressure medium lines with a valve (50) for feeding the control valve and in that the monitor (67) is connected to the power transmission part and so that it responds to the fluid pressure therein and that it controls the operation of the valve. 909 8 2 8/1078 6AD ORIGINAL 7. Drive according to claim 6, characterized in that that the valve is an electric valve and that the pressure monitor (67) has a switch (72) Contacts (90,91,98,99) for controlling the magnet which is dependent on the pressure in the power transmission part and actuates the valve. 8. Drive according to claim 6, characterized by a start holder (80) for the pressure monitor (67), which quickly energizes the magnet and the valve (50) opens quickly in order to apply pressure medium to the modulating piston (60) and the modulating pressure switch (72). 9. Drive according to claim 6, characterized by a plurality of at least three redundancy actuating devices (A, B, C, D) and in that their power transmission parts are connected to a common force summing element (63) are and that all power transmission parts (60) in the normal state at the output of the summing element to the effect come and that a reset device (64,65) corresponding to the middle position of the output of the summing element is active, whereby the error of a rotary motor (26) via a working lever (5 * 0 a control jet pipe (52) has the consequence that the resetting device (64,65) resets the jet pipe (52) perform and cause a greater than the working pressure, so that a creature in the · normal working pressure on the modulating piston (60) and the accompanying activity of the monitor (67) the effectiveness of the valve (50) ended. 10. Drive according to claim 9, characterized that the jet pipe for adjustment 90 9 828/1078 of the monitor (67) and the reset device (64,65) are set up to apply pressure. 11. Drive according to claim 1O _3, characterized in that the power transmission part contains a modulating piston (60) and that the monitor causes the position of the jet pipe (52), which in the normal position in the channels (57 »58) generates the same high pressures, which Channels are connected to the end faces of the modulating piston (60) and bring the same pressures to effect in the normal position. 12. Drive according to claim 10, characterized by a pressure monitor (67) with a time "delay responds to the pressure which acts on the power transmission part and which together with the adjustable Jet pipe (52) is effective. 13. Drive according to claim S _3, characterized in that the valve (50) is an electromagnetic valve and that the pressure monitor (67) is assigned a switch (72) which controls the magnetic circuit and which reacts to continued large adjustments of the monitor (67) its normal position responds by opening the circuit, the valve goes into the closed position. 14. Drive with a control unit for a main drive with a device for actuating a control valve for this main drive, characterized through redundancy channels (A, B, C, D) to each of which a corresponding large auxiliary motor (60) belongs to which all 909828/1078 BATH ORIGINAL on a summing element. (63) act, which is connected to the main drive valve (50) is connected through a pressure monitor (67), with which a differential pressure in the auxiliary engines is generated to move them and by a pressure switch (93j94) for the supervisor who is at a very high pressure difference in this auxiliary motor - Is effective and actuates a failure switch (72), which is connected to the magnetic switch, so that the Beaufschlaguag of the servomotor with pressure medium and thus the activity of the servomotor is ended. 15. Drive according to claim 1, characterized by the connection of the monitor (-67) with the resetting device (64,65) and by vorgesapnnte springs (119 ^ 120) ₃ which only allow a movement of the monitor when the pressure of the pressure medium has reached a predetermined level Size reached. 909828/10 78
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