Drive on base of synchronized hydraulic cylinders, reaction nozzle of turbojet engine (versions) and turbojet engine

FIELD: aircraft industry; turbojet engines.

SUBSTANCE: proposed turbojet engine includes reaction nozzle with variable exit section and orientation determined by position of movable flaps, and drive on base of synchronized hydraulic cylinders. Drive contains hydraulic control system, drive hydraulic cylinder, at least one driven hydraulic cylinder and mechanical transfer device. Drive hydraulic cylinder has cylinder and piston forming two spaces in cylinder connected with hydraulic control system. Driven hydraulic cylinder contains cylinder and piston determining two spaces in cylinder at least first space of which is coupled with output of distributor. Distributor is connected with hydraulic control system, and it contains control member whose position defines pressure in first space of driven hydraulic cylinder. Mechanical transfer device service to transmit displacement of piston of drive hydraulic cylinder to control member of distributor connected with driven hydraulic cylinder. Distributor is connected with driven hydraulic cylinder so that piston of driven hydraulic cylinder automatically follows piston of drive hydraulic cylinder by position command received from control member of distributor connected with driven hydraulic cylinder.

EFFECT: provision of simultaneous displacement of hydraulic cylinder rods, reduced mass of drive.

14 cl, 8 dwg

The technical field to which the invention relates.

The present invention relates to a turbojet engine, a jet nozzle of such a motor and to the actuator on the basis of synchronized hydraulic cylinders, which, in particular, can be used to move the movable shutters jet nozzle turbojet engine with adjustable output section. The invention can also be used for other purposes, for example, to move the control ring rotatable blades in a stationary guide apparatus of the compressor of the gas turbine.

The level of technology

In the famous jet nozzle with adjustable output section moving the movable sash is implemented using a system of hydraulic cylinders acting on a driven leaf, which, in turn, move the driven leaf. Managed sash move rods, pivotally connected with the cylinders or the General Manager of the ring affected by the cylinders. Mechanical tools provide synchronization of the shutters managed independently driven shutters, which are not managed. Such a jet nozzle with mechanical automatic synchronization system has drawbacks in terms of cost and weight, as well as due to the presence of interaction is many of the rubbing elements in a hot environment.

Another solution is to provide simultaneous movement of the valves with the elimination of friction and jamming between the wings, which would require increased efforts impact and could cause damage affecting the service life of the valves, due to the fact that the synchronization feature is moved to the level of the cylinders.

However, because of the inevitable variation in characteristics is almost impossible to achieve simultaneous movement of the cylinders even when the control cylinders from a common distributor of hydraulic fluid.

To solve this problem, in patent document France No. 2756329 it was proposed that the mechanical connection between the pistons of the cylinders with the help of the ring gear, scalawags with gears, each of which is connected with the piston of the hydraulic transmission "screw-nut"that converts the forward motion of the piston into rotation of the gear.

Such a device synchronization allows you to securely simultaneous displacement of the pistons of the cylinders. However, it requires use gear capable of transmitting the necessary effort to compensate for differences in the course of the pistons, that is relatively massive and bulky rings.

The invention

The main task, solved the e which directed the present invention, is to create a drive on the basis of synchronized hydraulic cylinders free from this drawback and intended for use in jet nozzles turbojet engine.

In accordance with the invention the solution of this problem is achieved through the creation of the actuator on the basis of synchronized hydraulic cylinders, containing:

hydraulic control system,

leading the cylinder containing the cylinder and the piston defining in the cylinder twin cavity associated with a hydraulic control system,

at least one slave cylinder containing cylinder and a piston defining in the cylinder two cavities, of which at least the first cavity is connected with the output of the distributor, and the specified valve associated with the hydraulic control system and contains the governing body, the position of which determines the pressure in the first cavity of the slave cylinder, and

the mechanical transmission device for transmitting movement of the piston of the master cylinder on the governing body of the distributor associated with the slave cylinder so that movement of the piston of the slave cylinder automatically follows the movement of the piston of the master cylinder on the basis of the command position, coming from the governing body of the RA is pridesites, associated with the slave cylinder.

Therefore, at the level of each slave cylinder specified position of the master cylinder is transmitted by mechanical means acts directly on the piston of the slave cylinder, and a valve associated with the slave cylinder and acting as a hydraulic amplifier mechanical signal to its set position. Due to this, the mechanical transmission device, which serves to move the piston of the master cylinder, can be provided more light means.

According to the features of the actuator according to the invention is a gear reduction device comprises: a device for converting the translational movement of the piston of the master cylinder into rotational movement of the pinion, the transmission device rotational motion of the pinion on the driven gear and device for converting rotational motion of the driven gear in the forward movement of the governing body of the distributor (i.e. valve)associated with one or each of the slave cylinder.

Ideally, a device converting rotational motion of the driven gear in the forward movement of the governing body formed by the first conveying screw-and-nut in which the screw is connected with the managing authority is m (spool). Also provided second gear "screw-nut" to convert linear movement of the piston of the slave cylinder, acting as a nut, a rotary motion of the second gear screw "screw-nut". When the slide valve and the second gear screw "screw-nut" swiney with each other so that rotation of the valve and screw cancel each other out and the spool does the progressive movement, when the movement of the piston of the master cylinder is transmitted to the spool, and the movement of the piston of the slave cylinder is synchronized.

Device transmit rotational motion of the pinion on the driven gear is made, for example, in the form of a flexible linear transmission bearings rolling bearing toothed rack which engages the pinion.

One or each of the slave cylinder can include a first cavity associated with the dispenser, which refers to the slave cylinder, and a second chamber which is hydraulically connected to the cavity of the master cylinder.

In the embodiment, each slave cylinder connected two-way valve associated with the first and second cavities of the slave cylinder.

In that case, when the pistons of the hydraulic cylinders connected to a single control ring, the actuator preferably contains one leading hydroc is link and two slave cylinder. If there is a need for additional hydraulic cylinder, the additional hydraulic cylinder can be a companion cylinder connected to a hydraulic control system in parallel to the master cylinder. In this case the presence of one master and two slave cylinders sufficient to provide the desired synchronization.

The invention also covers an embodiment of the jet nozzle turbojet engine, which has adjustable output section and the orientation determined by the position of the movable sash, and which contains an actuator made in accordance with options, envisioning adjustable offset.

The invention comprises, in addition, an alternative embodiment of a jet nozzle of a turbojet engine, which has an adjustable output section defined by the position of the movable sash, and which contains an actuator made in accordance with any of the other methods.

Further, the invention encompasses a turbojet engine, containing the above-described actuator on the basis of synchronized hydraulic cylinders.

List of figures

The invention will be clearer from the following detailed description does not limit the invention and steriade what about the references to the accompanying drawings, on which:

figure 1 depicts a block diagram of the actuator according to the invention in the example of its use for jet nozzle flaps adjustable section,

figure 2 depicts a view in partial section the master cylinder actuator according to the invention,

figure 3 shows in enlarged scale a part of the cylinder of figure 2,

figure 4 depicts a partial view of a section along the plane IV-IV of figure 3,

figure 5 depicts a view in partial section the slave cylinder of the actuator of figure 1,

6 depicts in enlarged scale a part of the cylinder in figure 5,

7 is a diagram illustrating the principle of operation of the actuator of figure 1,

Fig is a block diagram of the actuator according to the invention in the exemplary embodiment for the valves vector jet nozzle.

Information confirming the possibility of carrying out the invention

This description refers mainly to the example of using the invention, the actuator movable flaps or folds, such as movable sash nozzle turbojet engine with adjustable output section.

1 schematically depicts the actuator in accordance with the invention, containing sets (master) cylinder 10, two of the slave cylinder 20, the companion cylinder 30, the gear reduction device 40 between the master and two slave cylinders gidravlicheskiy control system (hydraulic unit 50 controls the nozzle).

In the shown example, the execution of the cylinders 10, 20 and 30 act on the control ring 60, to which the hinge is attached thrust 62 connecting the control ring 60 with movable shutters 64 nozzles. Figure 1 presents one rod 62 and one shutter 64, and the drive and the control ring are presented in the scan plane.

The total number of cylinders is chosen preferably to be equal to three for the formation of a static system. When choosing the three cylinders one is leading, and the other two slaves, i.e. the movement of their pistons depends on the displacement of the master cylinder. If the system has more than three cylinders in order to ensure that the effort required for displacement of the control ring without undesirable increase the size of the cylinders, an additional hydraulic cylinder or cylinders can be accompanied by hydraulic cylinders (in the exemplary embodiment of figure 1 has one accompanying the cylinder). The accompanying power cylinder or cylinders made from hydraulic control system, parallel to the master cylinder, the degree specified synchronization can be achieved leading cylinder and two slave cylinders.

It should be noted that the actuators can be used without a control ring, that is, g is gracilenta may be connected by rods directly with leaves or other organs who needs to synchronously operate.

In the example of execution shown in detail in figures 1 and 2, the master cylinder 10 includes a cylinder 100 with the piston 102, which is mounted movably along the axis of the cylinder and rigidly connected to a rod 104, the end of which is connected with the control ring 60 by a hinge 106. This stem Assembly 104 with the piston 102 is directed at the movement of the bearing 101, tightly closing the cylinder 100. The linear position sensor, comprising a housing 105 that is associated with the cylinder 100, and the rod 107 fixed in the cavity a rod 104, allows to measure the position of the shaft 104 along the length of the stroke of the hydraulic cylinder. The signal generated by this sensor position is the actual position of the movable sash and transmitted to the control device by the configuration of the nozzle. Its rear end opposite the cavity for placement of the rod 104, the cylinder 100 mounted on the wall 70 by a hinge 110.

The piston 102 divides the internal volume of the cylinder 100 into two cavities 112 and 114. The rear cavity 112 is connected with the hydraulic unit 50 control nozzles hydroline 120, and the front cavity 114 is associated with the specified block 50 management hydroline 122.

The transmission 130 "screw-nut" converts the translational displacement of the piston 102 into rotational motion (figure 2). In the transmission 130 nut 132 is made in the form of a cylindrical crucial is I, one end of which is rigidly connected to the paw 134 rigidly connected, in turn, with the rod 104 of the piston. At the other end of the rod 132 is made blind axial groove 136, threaded 138, at least part of its length. The rod 132 can slide in the cavity 140 formed in the housing 142 which is rigidly connected with the cylinder body 100, for example, are molded as one piece with the body.

The screw 144 transmission 130 "screw-nut" has an end portion 144A threaded and enters the groove 136 of the nut 132. The other end 144b of the screw, without threads, is held in the bearing 146 mounted in the housing 142.

The screw 144 causes the rotation of the pinion gear 150 within the housing 142. Gear 150 may be mounted directly on the end of the screw 144 or, as shown in figure 2, it can be installed on the end of the rod 152, which is connected to the screw 144 for joint rotation, but may move along the axis relative to him. The connection between the screw 144 and the rod 152 to ensure joint rotation can be performed, for example, in the form of interactive flat sections (flats) and faces the response form, completed on parts of the screw 144 and rod 152. To convert rotary motion into reciprocating without jamming can be used by any other mechanical means, and these means are not necessarily dollars which have to be accurately centered on the axis. The rod 152 is installed in the bearing 154 inside the cover attached to the housing 142. This solution simplifies the installation of the pinion 150.

Leading gear 150 engages with the cut gear rack 402 mechanical transmission devices 40 (Fig 3 and 4).

In the exemplary embodiment of figure 2 the tracking system of the movement of the piston 102 is transmitted to the gear 150 is located at the side of the cylinder 100.

In an embodiment using at least one accompanying cylinder sensor 105 may be installed along the axis of the companion cylinder, and then in the master cylinder 100 remains for placement along the axis of the transmission 130, as shown in figure 1. In this case, the master cylinder 10 can be made more compact.

Gear reduction device 40 in the best case scenario is formed by a flexible linear transfer 400 on rolling bearings, for example, this type of as the transfer of the brand "Teleflex Syneravia" French firm Intertechnique. Flexible linear transfer contains a flexible metal strip 404, which slides between the two strips 406, 408, based on the balls or rollers 410, 412, while the entire device is enclosed in a hard protective casing 414.

At the site of interaction with the pinion 150 casing 414 and one tape 406 is cut out, and cut the ends of the tape are bent inward and close the cavity of the placement of the balls 10. Cut the rack 402 is rigidly attached, for example welded, to the exposed portion of strip 404 and slides along with it. Protective box 416 closes the rack 402, its connection with the rest of the linear transmission 400 and pinion gear 150. Box 416 attached to the cylinder 10 and the casing 414. The rod 152, which carries the gear 150, passes through the bearing 418 mounted in box 416. In figure 4, as in figure 1, gear reduction device 40 provided in the form of a sweep on the plane.

Each slave cylinder 20 (Fig 1, 5 and 6) contains the cylinder 200 with piston 202, which is mounted movably along the axis of the cylinder and is rigidly connected with the rod 204, which is connected with the control ring 60 by a hinge 206. At its anterior end of the cylinder 200 is closed by the bearing 201 rod, through which firmly held the rod 204. Its rear end opposite the cavity for placement of the rod 204, the cylinder 200 is mounted on the wall 70 by a hinge 210.

The piston 202 divides the internal volume of the cylinder 200 on two cavity 212 and 214 (Fig.7). The rear cavity 212 is connected with the hydraulic unit 50 control nozzles hydroline 220, and the front cavity 214 is operated valve 260, the output of which is connected with the cavity 214 hydroline 216.

The dispenser 260 (6) contains the cylinder 262, inside of which is mounted for sliding the spool 264 is laskami 266, 268 for management (higher) deadlift, forming a three cavity 270, 272, 274. Their ends dispenser associated with hydroline 276 with the release of BP low pressure unit 50 controls, while the intermediate cavity of the distributor is connected by hydroline 278 with the release of HP high pressure unit 50 controls. Thus, in the intermediate cavity of the dispenser to create the same pressure as the pressure in the cavity 114 of the master cylinder that serves as a reference pressure. Depending on the axial position of the spool 264 dispenser 260 sets the message of the cavity 214 of the cylinder or hydroline 276 or hydroline 278.

In addition, the cavity 214 of the hydraulic cylinder 20 is connected by means of two parallel, connected in opposite safety valves 280, 282 with hydroline 222, going to the block 50 control (Fig.7). Due to this, the pressure in the cavity 214 of the slave cylinder is not too can deviate from the value of the pressure in the cavity 114, which serves as the reference pressure. Otherwise one would run the risk of "twisting" of the nozzle.

Transmission 230 "screw-nut" (figure 5, 6) converts the translational movement of the piston 202 in the rotational movement. In this system, the nut 232 is rigidly connected with the piston rod 204 and is dead in the longitudinal groove 234, which is made in the stem 204 and is open to its rear end. Nut 232 is only cha is th grooves 234 near its open end.

Screw 236 transmission 230 has a tail section a with thread, which is screwed in the nut 232 and can be carried further into the groove 234 (figure 5). On the rear end section 236b without thread screw 236 is supported in the bearing 238 prescribed in the support 240 is rigidly attached to the body 242 of the cylinder 200.

Screw pair 232-236 transmission 230 "screw-nut" identical coil pair 132-144 transmission 130 "screw-nut" and has the same purpose, that is, through these pairs of forward movement of the pistons master and slave cylinders is converted into rotational movement of the screws 144 and 236.

At its end section 236b screw 236 has an axial blind groove 244 with a thread into which is screwed the threaded end of the valve 264 dispenser 260 (6). Thus, the valve 264 and the screw 236 to form another "screw-and-nut in which the nut is formed by a screw 236 transmission 230 "screw-nut". In this third gear 264-236 "screw-nut" screw step has the same direction as in the transmission 230.

At its other end the valve 264 is connected to the rod 246 with the possibility of joint rotation, but allowing free relative displacement along the axis. Communication between the control valve 264 and the end of the rod 246 may be performed, for example, in the form of interactive flat sections (flats) and faces the response form, completed by the relevant parts of the elements of the s 264, 246. To convert rotary motion into reciprocating without jamming can be used by any other mechanical means, and these means need not be precisely centered on the axis. At its other end the rod 246 carries the driven gear 250. The rod 246 is installed in the bearing 248 the inside of the cover 254 mounted on the housing 252.

Driven gear 250 engages with the length of the rack 420 gear reduction device 40. Installation cut the rack 420 and its relation with the driven gear 250 are carried out in the same manner as described above with respect to the segment rack 404 and leading gear 150.

Accompanying the hydraulic cylinder 30 (Fig 1) contains the cylinder 300 with the piston 302, which is mounted movably along the axis of the cylinder and is rigidly connected with the rod 304 associated with the control ring 60 by a hinge 306. Its rear end opposite the cavity for placement of the rod 304, the cylinder 300 mounted on the wall 70 by a hinge (not shown).

The piston 302 divides the internal volume of the cylinder 300 into two cavities 312 and 314. The rear cavity 312 is connected with the hydraulic unit 50 control hydroline 320, and the front cavity 314 is connected with the hydraulic unit 50 control hydroline 322.

The hydroline 120, 220, 320 jointly connected to the output S0 of the block 50, and a hydroline 122 222 and 322 are jointly connected to a different output (S1) of the block 50.

Thus, the master cylinder 10 and the guide cylinder 30 feed fluid medium in parallel. As for the slave cylinders 20, the cavity 212 are fed in parallel with the cavities 112 and 312 of the cylinders 10 and 30, and the cavity 214 are fed from the distributor 260.

Next will be described the operation of the actuator according to the invention with reference to Fig.7, which shows a schematic diagram of this system (except for accompanying cylinder 30) and some elements of the block 50.

The pump 502, called the pump nozzle, a high pressure HP, is designed to actuate the cylinder to impact the movable sash to increase (open) or decrease (closing) of the output section of the nozzle, through which are derived gases. In this case, is provided by the use of a special pump 502 to generate a high pressure, which greatly exceeds the high pressure provided by the pump 504 high pressure General hydraulic system turbojet engine.

High pressure HP is supplied to the output S0 or output S1 using servo valve 500, in which the pressure HP filed at its input 512, and outputs 514, 516 are connected to the outputs S0, S1. You can use the servo valve with two steps 500A, 500b. High pressure HP communicated by the second stage 500b team first stupen the 500A. The inputs 518, 520 stage 500A also submitted to the high pressure hp of the pump circuit 504 and the low pressure BP from the pump 522 low pressure General hydraulic system. The first stage is controlled by the signal S, for example, an electric signal to control the hydraulic distributor.

High and low pressure HP, BP outputs from the control unit 50 is sent to the distributors of the slave cylinders on the hose 278 and 276, respectively.

Supply high pressure HP output S0 command in the form of a signal S causes, for example, the opening of the nozzle, and the output S1 is fed to the low pressure BP. High pressure HP is fed parallel to the cavity 112, 212 and 312 of the cylinders 10, 20, 30, while their cavity 114, 214, 314 are under low pressure BP. With increasing levels of pressure HP and BP modulated depending on the transmitted nozzle efforts through the servo valve 500 (with respect to the cavities 112 and 114, 212, 312 and 314) and distributors 260 (with respect to the cavities 214). Pressure flow HP or BP in the cavity 114, 214 is controlled by the position control deviation between the master and slave cylinders, i.e. the error in the regulation.

The movement of stem 104 of the master cylinder is copied to each slave cylinder 20 through the transmission 130 "screw-and-nut, pinion 150, a flexible linear transmission 400 and driven gear 250.

Rotations is the driven gear 250 is transmitted through the rod 246 to the spool 264 control valve 260. Due to the thread of the axial grooves 244 of the screw 236 spool 264 forms a transfer of "screw-nut", which converts the rotation of the spool in its forward movement so that the pressure BP is fed into the cavity 214 of the cylinder.

When moving the piston 202 of the cylinder to its translational motion is converted into rotational movement of the screw 236.

Any desynchronization of the translational motion of the pistons 102, 202 is converted into an axial displacement of the valve 264, which thereby modulating the pressure supplied to the cavity 214 for rapid compensation of this desynchronization.

The direction of action of the belt 268 dispenser 260 under pressure supplied by hydroline 216, chosen in accordance with the direction of the screw step 244 and 236 to feedback in a tracking system was carried out in the right direction with regard to the level of pressure in the hose 276 and 278.

Step screw to couple the spool 264 - groove 244 is selected to meet the pitch is for a pair of screw 236 - nut 232 so that when the movement of the pistons 102 and 202 are synchronized, the rotation of the screw 236 forming screw feedback compensates for the rotation of the spool 264, and the latter remains in a stationary position, i.e. in equilibrium in respect to translational motion.

The desired thread pitch of the groove 244 may be defined as follows.

Maximum hydraulic amplification of the valve should be achieved when the position control deviation between the slave and the leading cylinders reaches a certain maximum value which is a function of the mechanical ability of the nozzle to withstand the deformation of the" without jamming and without risk of permanent deformation of the parts, and the ability of the aircraft to withstand jet thrust that is offset relative to its axis.

On the basis of the maximum quantity of hydraulic amplification of the distributor 260, which can be translated into the maximum stroke of the valve 264 (comprising, for example, 1 mm), and the level of acceptable mismatch synchronization between the cylinders, which can be translated to a percentage of the stroke of the pistons (for example, 2%), can be installed step thread grooves 244 given the fact that the screw pitch of the gears 130 and 230 "screw-nut" is chosen from the condition of reversibility of their ongoing convert linear motion into rotational.

In addition, for the rack 402 selects a relatively long stroke, for example, amounting to a few centimeters, in order to reduce the influence of gaps or bends at the level of the gear reduction device 40. This move allows us to determine the diameter of the gears 150 and 250.

Supply high pressure HP output S1 command in the form the of ignal S causes the closing of the nozzle, the output S0 is fed to the low pressure BP.

Synchronizing the displacement of the pistons of the cylinders 10 and 20 is the same as described above.

7 the arrows indicate the direction of movement of the elements and flow of the fluid followed by retraction of the piston 104 of the master cylinder when the "right" step all screws.

Thus, the actuator in accordance with the invention has the distinguishing feature that the mechanical transmission device that copies the movement of the master cylinder is not exposed to significant loads. This transfer device copies the movement of the master cylinder and passes it to the governing body of the distributor, which acts as a hydraulic amplifier. Indeed, the driven gear rotates in conjunction with the governing body (disc) dispenser, which has no direct kinematic connection with a nut rigidly connected to the piston of the slave cylinder.

Due to this gear reduction device can be much easier compared with devices that use sprockets located in the mechanical kinematic connection with the pistons of the cylinders.

In addition, it appears sufficient to manage, through a distributor, the pressure in only one of palaste the slave cylinders. Pressure control in the two cavities of the slave cylinders through distributors, driven from the master cylinder, can be provided, but is not necessary.

The use of flexible linear transmission bearings rolling is advantageous because of its low weight, ability to provide effective mechanical synchronization without impact to manufacturing errors, and thermal expansion, but also due to its durability. You can also use other means of mechanical transmission with a gear meshing with gears, such as gear or flexible shafts with endless screws. Due to the low effort required synchronization becomes possible to reduce the sizes of these elements.

In the above description illustrates the use of the system according to the invention as applied to a movable shutters jet nozzle with variable cross-section.

As already indicated, the invention is not limited to this application and can be used to control the hydraulic cylinders moving bodies not only of the valves, and other components that must move synchronously, or to control valves rotary jet nozzles ("nozzle with thrust vector control").

In this latter case, the leaf swivel jet nozzle are controlled by the use of three cylinders, synchronized, at least mechanically and has two device adjustable offset, which are controlled by electrical means and affect the position of the two respective cylinders in order to change it's position relative to managed provisions of the third cylinder, with the aim of orienting the nozzle.

This exemplary embodiment is schematically represented in Fig. The same elements in figure 1-7 and 8 are denoted by the same positions.

The drive Fig contains the master cylinder 10 and two of the slave cylinder 20 with a mechanical gear device 40 between the master and slave cylinders. The cylinders 10, 20 and gear reduction device 40 similar to that described above.

The device 71 adjustable bias built between mechanical gear device 40 and each of the slave cylinder 20. On Fig detail shows only one device 71 adjustable offset.

The device 71 adjustable offset contains gear 702, the axis of which coincides with the axis of the spool 264 dispenser 260 corresponding slave cylinder 20. On its outer side surface of the crown 702 engages with a toothed rack 420 transfer device 40.

On its inner side surface of the crown 702 engages with the satellite gear 704, placed the military between the crown 702 and gear hub 706 gear 708, concentric with the spool 264 dispenser 260.

Gear 704 is installed with the possibility of free rotation on the axle 710, which is connected via a shoulder 712 with the rod 246 and forms together with it drove. Thus the axis of the axle 710 parallel to the axis of the rod 246, but radially offset from it. Thus, unlike the example running on 6 and 7, the rod 246 which rotates together with the spool 264 dispenser is in kinematic connection with the rack 420 through not only driven gear 250, but also with gear 704 and crown 702.

Gear 708 is connected to the output shaft 714 stepper motor 716. The computing device 80 of the thrust vector control delivers the engine control signal 716 input angular displacement between the rod 246 and the rack 420 by rotating gears 708 and gear 704. This angular offset is determined in the function control command on the orientation of the nozzle, supplied by the flight control system. It should be noted that in the presented example of executing a very high reduction ratios relative to the engine 716 allows a simple stepper motor without gear.

Team vector controller are superimposed on the control command output section from the computing device 90. This computational condition is the device 90 receives from the master cylinder 10 and information about the position of the sash, and supplies the control unit 50 of the necessary control signals to obtain the desired output section by simultaneous exposure to fold the master and slave cylinders.

Provided by the link in the dialog between computing devices 80 and 90 to optimize engine operation mode in accordance with control commands orientation and power.

Thus, the use of a synchronization system according to the invention provides two significant benefits:

- due to the presence of hydraulic amplification at the level of the slave cylinders electric tools tracking automatic control of the displacement of the position associated with the slave cylinders and, therefore, can operate at a lower power level, and

- in case of failure of the electric control circuit of the nozzle, the system returns to the mode of mechanical synchronization of the cylinders, which is a safe fallback position (the nozzle is not blocked in any position other than neutral).

1. The actuator on the basis of synchronized hydraulic cylinders, characterized in that it includes a hydraulic control system (50), a leading cylinder (10)containing the cylinder (100) and the piston (102)that defines the two cylinder cavity, associated with a hydraulic control system, at least one slave cylinder (20)containing the cylinder (200) and the piston (202)defining in the cylinder two cavities, of which at least the first bands of the b connected with the output of the distributor (260), associated with the hydraulic control system and contains the governing body (264), the position of which determines the pressure in the first cavity of the slave cylinder, and a mechanical transmission device (40) for transmitting movement of the piston (102) of the master cylinder (10) of the governing body (264) of the distributor (260)associated with the slave cylinder (20) in such a way that the movement of the piston (202) slave cylinder (20) automatically follows the movement of the piston of the master cylinder on the basis of the command position, coming from the governing body of the distributor associated with the slave cylinder.

2. The actuator according to claim 1, characterized in that the mechanical transmission device includes a device (130) convert linear movement of the piston (102) of the master cylinder (10) in the rotational movement of the pinion (150), the device (400) transmission of the rotational movement of the pinion (150) on the driven gear (250) and device for converting rotational motion of the driven gear in the forward movement of the slide valve (264) of the distributor associated with one or each of the slave cylinder.

3. The actuator according to claim 2, characterized in that the device for converting rotational motion of the driven gear (250) in the forward movement of the slide valve (264) founded the first gear is th "screw-nut", in which the screw is rigidly connected to the valve.

4. The actuator according to claim 3, characterized in that it contains a second transfer of the "screw-nut" to convert linear movement of the piston (202) slave cylinder (20)acting as a nut, a rotary motion of the screw (236) second gear "screw-nut", and the spool (264) and screw (236) second gear "screw-nut" swiney with each other so that rotation of the spool (264) and screw (236) are mutually compensated, and the spool does the progressive movement, when the movement of the piston of the master cylinder, passed on the spool, and the movement of the piston of the slave cylinder is synchronized.

5. The actuator according to claim 2, characterized in that one or each of the slave cylinder (20) contains a first cavity (214)associated with the distributor (260)related to this slave cylinder, and a second cavity (212), hydraulically connected with the cavity (112) of the master cylinder.

6. The actuator according to claim 2, characterized in that the distributor relating to one or to each slave cylinder is a two-way valve associated with the two cavities of the slave cylinder.

7. The actuator according to claim 2, characterized in that the transfer device and the rotational motion of the pinion (150) on the driven gear (250) is made in the form of a flexible linear transmission (400) op the arts rolling, carrier rack which engages the pinion.

8. The actuator according to claim 1, characterized in that all the pistons of the cylinders are connected with the control ring (60), and the drive contains one leading cylinder (10) and two slave cylinder (20).

9. The actuator of claim 8, characterized in that it contains additional accompanying the hydraulic cylinder (30), fed by a hydraulic control system in parallel to the master cylinder (10).

10. The actuator according to claim 1, characterized in that it contains a device (71) adjustable offset, built between the mechanical transmission device and the managing authority (264) slave cylinder (20) to enable input of shift between the position of the slave cylinder (20)installed in the tracking mode, and the specified position of the master cylinder (10).

11. The actuator according to any one of claim 2 to 10, characterized in that the device (71) adjustable offset is made in the form of a device providing angular displacement between the spool (264) slave cylinder (20) and ring gear (702)kinematically associated with the device (400) transmission of rotational motion from the driving gear (150).

12. Jet nozzle of the turbojet engine having adjustable output section, which is determined by the position of movable shutters, characterized in that it contains the drive on which the yubom one of claims 1 to 9 for simultaneous movement of the movable sash.

13. Jet nozzle of the turbojet engine having adjustable output section and orientation, which are determined by the position of movable shutters, characterized in that it contains the actuator of claim 10 or 11 to move the movable shutters.

14. Turbojet engine, containing the actuator on the basis of synchronized hydraulic cylinders made in accordance with any of claims 1 to 11.