EP1331404A1 - Ensemble d'actionnement à vérins hydrauliques synchronisés - Google Patents
Ensemble d'actionnement à vérins hydrauliques synchronisés Download PDFInfo
- Publication number
- EP1331404A1 EP1331404A1 EP03290036A EP03290036A EP1331404A1 EP 1331404 A1 EP1331404 A1 EP 1331404A1 EP 03290036 A EP03290036 A EP 03290036A EP 03290036 A EP03290036 A EP 03290036A EP 1331404 A1 EP1331404 A1 EP 1331404A1
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- EP
- European Patent Office
- Prior art keywords
- cylinder
- pilot
- piloted
- piston
- screw
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/22—Synchronisation of the movement of two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
- F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/16—Systems essentially having two or more interacting servomotors, e.g. multi-stage
Definitions
- the invention relates to the synchronization of hydraulic cylinders and finds an application in particular for the simultaneous actuation of movable flaps of jet nozzles of variable ejection section.
- the invention can however be used in other applications, for example example for actuating an angle vane control ring variable timing in a fixed turbine compressor rectifier gas.
- the actuation of the movable flaps is carried out by means of a set of hydraulic cylinders acting on controlled shutters, which in turn lead to follower flaps.
- the shutters ordered are actuated by links articulated on the rods of the cylinders or on a common control ring on which the jacks act. of the mechanical means ensure synchronization of the controlled shutters, regardless of follower components which are not.
- Such a nozzle whose mechanical design makes it self-synchronized, has disadvantages in terms of cost and mass and due to the presence of parts caused to rub on each other hot.
- Another solution is to order all the shutters in synchronism to avoid friction or even jamming between flaps that require increased actuation effort and can be causes of damage affecting the life of the shutters, postponing the synchronization function at the cylinders.
- Such a synchronization device makes it possible to ensure a simultaneous displacement of the pistons of the cylinders but requires a ring toothed capable of transmitting the efforts necessary to defeat the displacement differences between pistons, so a relatively massive ring and bulky.
- the object of the invention is to provide an actuation assembly for synchronized hydraulic cylinders not having such a drawback.
- this mechanical transmission includes a device for converting the translational displacement of the piston of the pilot cylinder in movement in rotation of a pilot gear, a movement transmission device of rotation of the pilot pinion to a piloted pinion, and a device for conversion of the rotational movement of the driven pinion into a displacement in translation of a control rod of the distributor associated with or each actuated cylinder.
- the device for converting the movement of rotation of the driven pinion in a translational movement of the rod control is formed by a first screw-nut system in which the screw is carried by the control rod. It is then planned a second screw-nut system to convert a displacement in translation of the piston of the actuated cylinder, acting as a nut, in a rotational movement of the screw of the second screw-nut system, the control rod and the screw of the second screw-nut system being screwed one on the other so that the rotations of the control rod and the screw compensate each other and that the control rod remains stationary in translation when the displacement the piston of the pilot cylinder, transmitted to the control rod, and that of the piston of the actuated cylinder are synchronized.
- the device for transmitting the rotational movement of the pilot pinion to a piloted pinion is for example constituted by a flexible linear bearing with racks on which mesh the pinions.
- the or each actuated cylinder can have a first chamber connected to the distributor associated with this piloted jack and a second chamber connected in common with a pilot cylinder chamber.
- the actuation assembly preferably comprises a jack pilot and two piloted cylinders. If at least one additional cylinder is necessary, this additional cylinder may be a follower cylinder connected to the hydraulic circuit in parallel with the pilot cylinder, the presence of a cylinder pilot and two piloted cylinders being sufficient to ensure the synchronization desired.
- Figure 1 shows an actuation assembly according to the invention comprising a pilot cylinder 10, two piloted cylinders 20, a cylinder follower 30, a mechanical transmission device 40 between the jack pilot and piloted cylinders and a hydraulic nozzle control unit 50.
- the jacks 10, 20 and 30 act on a control ring 60 on which are articulated rods 62 connecting the control ring 60 to movable nozzle flaps 64 (one single link 62 and a single flap 64 are shown in Figure 1 which is a plan view of the actuation assembly and of the control ring).
- actuation assembly can be used without a control ring, the cylinders being connected by rods directly to the flaps or other movable members to move in synchronism.
- the pilot cylinder 10 comprises a cylinder 100 with a piston 102 axially movable in the cylinder and integral with a rod 104 connected to a end to the control ring 60 by a hinge 106.
- This rod 104 and piston 102 assembly is guided in translation by a bearing watertight 101 closing off the cylinder 100.
- a linear position sensor having a body 105 linked to the cylinder 100 and a rod 107 fixed in a bore 104a of rod 104 makes it possible to measure the position of rod 104 over the entire stroke of the cylinder.
- the signal provided by this position sensor represents the actual position of the movable flaps and is transmitted to a unit the configuration of the nozzle.
- the cylinder 100 is mounted on a wall 70 by means of a hinge 110.
- the piston 102 shares the internal volume of the cylinder 100 in two chambers 112, 114.
- the rear chamber 112 is connected to the block hydraulic control of the nozzle 50 by a pipe 120 while the front chamber 114 is connected to the block 50 by a pipe 122.
- a screw-nut system 130 transforms the movement of linear translation of the piston 102 in rotational movement.
- the nut 132 is in the form of a cylindrical rod which, at one end is fixed to a lug 134 integral with the piston rod 104.
- a blind axial bore 136 which has a thread 138 over at least part of its length.
- the rod 132 can slide in a housing 140 formed in a body 142 integral with the body of the cylinder 100, for example molded in one piece with this one.
- the screw 144 of the screw-nut system 130 has an end portion threaded 144a engaged in the bore 136 of the nut 132. At its other end, not threaded 144b, the screw 144 is carried by a bearing 146 fixed in the body 142.
- the screw 144 rotates a pilot pinion 150, outside the body 142.
- the pinion 150 can be mounted directly to the end of screw 144 or, as illustrated in Figure 2, be mounted the end of a rod 152 integral in rotation with the screw 144 but free in axial translation relative thereto.
- the rotating connection between the screw 144 and the rod 152 is produced for example by square or formed flats in parts of the screw 144 and the rod 152 of forms mutually committed. Any other mechanical means allowing to transmit a rotational movement without jamming between two parts that are not necessarily exactly aligned may be used.
- the rod 152 is supported by a bearing 154 housed in a fixed cover on the body 142. This arrangement facilitates the mounting of the pinion pilot 150.
- Pilot sprocket 150 meshes with a rack segment 402 of the mechanical transmission device 40 ( Figures 3 and 4).
- the system 130 of copy of the movement of the piston 102 towards the pinion 150 is arranged laterally with respect to cylinder 100.
- the position sensor 105, 106 can be mounted axially in the cylinder follower, leaving the space available to house the system 130 axially relative to cylinder 100, as shown schematically on the Figure 1, so that the pilot cylinder 10 can be more compact.
- the transmission device 40 is advantageously formed by a flexible linear bearing 400, for example of the type marketed by the French company Intertechnique under the name "Teleflex Syneravia”. It has a flexible metallic core 404 which slides between two bands 406, 408 with interposition of balls or rollers 410, 412, the assembly being housed in a fixed sheath 414.
- the sheath 414 and one 406 of the strips are cut, the ends cut from the band 406 being folded to close the housing of the balls 410.
- the 402 rack segment is fixed, for example welded, on the part thus disengaged from the core 404 so as to slide integrally with the latter.
- a protective housing 416 encloses the rack 402, the areas of connection with the rest of the linear bearing 400 and the pilot pinion 150.
- the housing 416 is fixed to the jack 10 and to the sheath 414.
- the rod 152 carrying the pinion 150 passes through a bearing 418 carried by the housing 416.
- the transmission device 40 is represented in a form developed flat.
- Each actuated cylinder 20 ( Figures 1, 5 and 6) has a cylinder 200 with a piston 202 movable axially in the cylinder and integral a rod 204 connected to the control ring 60 by a hinge 206. At its front end, the cylinder 200 is closed by a rod bearing 201 tightly crossed by the rod 204. At its opposite rear end to that from which the rod 204 projects, the cylinder 200 is mounted on the wall 70 via a joint 210.
- the piston 202 shares the internal volume of the cylinder 200 in two chambers 212, 214.
- the rear chamber 212 is connected to block 50 by a line 220 while the front chamber 214 is supplied by a distributor 260, the outlet of which is connected to chamber 214 by a driving 216.
- the distributor 260 includes a cylinder 262 inside of which a control rod 264 carrying shoulders 266, 268 can slide and delimit three chambers 270, 272, 274. At its ends, the distributor is connected by a line 276 to a low pressure outlet BP hydraulic block 50, while in its intermediate chamber, it is connected by a line 278 to an HP hydraulic high pressure outlet of block 50 in order to collect an image pressure of that prevailing in the chamber 114 of the pilot cylinder, serving as reference pressure. According to axial position of the control rod 264, the distributor 260 puts the chamber 214 of the jack in communication with line 276 or with the driving 278.
- the chamber 214 of the jack 20 is further connected, via two valves overpressure 280, 282 mounted head to tail, to a line 222, itself connected to block 50.
- the pressure in chamber 214 of the piloted cylinder cannot deviate too much from chamber pressure 114 serving as a reference, otherwise a "twist" of the nozzle could be generated.
- a screw-nut system 230 transforms the movement of linear translation of the piston 202 in rotational movement.
- the nut 232 is integral with the piston rod 204 and is engaged in a blind longitudinal bore 234 formed in the rod 204 and opening at the rear end thereof.
- the nut 232 extends over a only part of the length of hole 234, in the vicinity of its opening.
- the screw 236 of the screw-nut system 230 has a threaded part 236a which is screwed into nut 232 and can extend into hole 234. A its rear end not threaded 236b, the screw 236 is carried by a bearing 238 mounted in a bearing support 240 integral with the body 242 of the cylinder 200.
- the screw thread 232-236 of the screw-nut system 230 is identical with the thread 132-144 of the screw-nut system 130, and has the same meaning, of so that the same displacement in translation of the pistons of the pilot cylinders and piloted results in the same rotational movement of the screws 144 and 236.
- the screw 236 In its end part 236b, the screw 236 has a hole axial blind threaded 244 into which is screwed a threaded end of the control rod 264 of the distributor 260, so that the rod 264 and the screws 236 constitute another screw-nut system in which the nut is formed by the screw 236 of the screw-nut system 230. In this other system screw-nut 264-236, the thread is in the same direction as in the system 230.
- control rod 264 is integral with rotation of a rod 246 but free in translation relative to the latter.
- the connection between the control rod 264 and one end of the rod 246 can be made by square or flats formed in parts of the rods 264, 246 mutually engaged in complementary forms. Other mechanical means for transmitting a rotational movement without wedging between two parts not necessarily exactly aligned can be used.
- the rod 246 carries a driven pinion 250.
- the rod 246 is supported by a bearing 248 housed in a cover 254 fixed to the body 252.
- the driven pinion 250 meshes with a rack segment 420 of the mechanical transmission device. Development of the segment rack 420 and its connection to the driven pinion 250 are made of the same way as described above with reference to the segment of rack 404 and pilot gear 50.
- the follower cylinder 30 (FIG. 1) comprises a cylinder 300 with a piston 302 movable axially in the cylinder and integral with a rod 304 connected to the control ring 60 by a hinge 306. At its end rear opposite to that from which the rod 304 projects, the cylinder 300 is mounted on the wall 70 by means of a hinge (not shown).
- the piston 302 shares the internal volume of the cylinder 300 in two chambers 312, 314.
- the rear chamber 312 is connected to block 50 by a pipe 320 while the front chamber 114 is connected to the block 50 through a pipe 322.
- Lines 120, 220, 320 are connected in common to a output S0 of block 50, while lines 122, 222 and 322 are connected in common with another output S1 of block 50.
- pilot cylinder 10 and the follower cylinder 30 are supplied with hydraulic fluid in parallel.
- actuated cylinders 20 they have their chambers 212 supplied in parallel with chambers 112 and 312 of the cylinders 10 and 30 but their chambers 214 are supplied by the distributors 260.
- a pump 502 called a nozzle pump, produces the high HP pressure intended to actuate the jacks to act on the movable flaps in order to enlarge (open) or reduce (close) the ejection section gas through the nozzle.
- the use of a particular pump 502 is here designed to provide the necessary high pressure level which is significantly higher than hp supplied by a high pressure pump 504 of the general hydraulic circuit of the turbojet engine.
- the HP pressure is applied to the S0 output or to the S1 output by means of a servo-valve 510 which receives the HP pressure on a input 512.
- the outputs 514, 516 of the servo-valve 510 are connected to the outputs S0, S1.
- the HP pressure is switched by the second stage 510b under the first stage control 510a.
- the latter receives on inputs 518, 520 the pressure hp of circuit 504 as well as a low pressure BP supplied by a low pressure pump 522 of the general hydraulic circuit.
- the first stage is controlled by a signal S, for example a signal electric controlling a hydraulic distributor.
- HP and BP pressures leave block 50 and are sent to the distributors of the jacks controlled by lines 276 and 278.
- the transfer of the HP pressure to the S0 outlet, under the control of the signal S1 causes for example the opening of the nozzle, the output S1 then being at pressure BP.
- High pressure HP is applied in parallel in chambers 112, 212 and 312 of cylinders 10, 20, 30, while the chambers 114, 214 and 314 are at BP pressure.
- the HP and BP pressures are then modulated according to the transmitted forces by the nozzle, by the servo-valve 510 (towards the chambers 112 and 114, 212, 312 and 314) and distributors 260 (to rooms 214).
- the application of the pressure HP or BP in the chambers 114, 214 is governed by the difference position between pilot and piloted cylinders, i.e. by the error of regulation.
- the displacement of the rod 104 of the pilot cylinder is copied via the screw-nut system 130, the pilot gear 150, the linear bearing 400 and the piloted pinion 250 at each piloted cylinder 20.
- the rotation of the driven pinion 250 is transmitted to the rod of control 264 of the distributor 260 via the rod 246.
- the rod 264 forms, with the thread of the axial bore 244 of the screw 236 a screw-nut system transforming the rotation of the rod 264 into linear displacement in translation thereof, so that the pressure BP is transmitted to the chamber 214 of the actuator.
- the piston 202 of the cylinder 200 being moved, its movement of translation is converted into a rotational movement of the screw 236.
- the direction of action of the shoulder 268 of the distributor 260 on the pressure delivered by line 216 is chosen in accordance with the direction threads 244 and 236 for feedback from the servo act the right way given the pressure levels in the lines 276 and 278.
- the screwing pitch between the rod 264 and the thread of the hole 244 is chosen opposite that existing between screw 236 and the thread of the nut 232, so that when the displacements of the pistons 102 and 202 are synchronized, the rotation of the screw 236, forming a screw feedback, compensates for that of the rod 264 and it remains stationary in translation, in a state of equilibrium.
- This thread pitch 244 can be determined as follows.
- the maximum hydraulic gain of the distributor 260 must be obtained when the position difference between piloted cylinder and pilot cylinder reaches a determined maximum value depending in particular on the capacity nozzle mechanics to withstand "distortion" without jamming and without causing permanent deformation of parts and the ability to the aircraft to support a misaligned thrust.
- the thread pitch 244 can be established, knowing that the steps of the screw-nut systems 130 and 230 are imposed by necessity reversibility between the translational and rotational movements they convert.
- the actuation assembly according to the invention is remarkable in that the mechanical transmission device which copies the displacement of the pilot cylinder is not exposed to significant forces.
- This transmission device copies the movement of the pilot cylinder towards a distributor control unit which acts as an amplifier hydraulic.
- the driven pinion is coupled in rotation to the rod of control of the distributor which is not in direct engagement with a nut secured to the piston of the piloted jack.
- the mechanical transmission device can therefore be considerably reduced compared to devices using rings toothed in mechanical engagement with the pistons of the jacks.
- a flexible linear bearing is advantageous from because of its low weight, its ability to ensure synchronization efficient mechanics without tolerance and thermal expansion effect and of its lifespan.
- other transmission devices mechanical meshing with pinions could be used, such than rack ring or flexible shafts with worm, but with a reduced sizing due to low synchronization effort required.
- the invention is not limited to this application and can be used for control by hydraulic cylinders moving parts other than shutters to be moved synchronism, or for the control of adjustable nozzle flaps (or "Vector").
- the adjustable nozzle flaps are controlled by at least three mechanically synchronized cylinders supplemented by two shifting devices which are slaved electrically and act on the set position of two cylinders corresponding to offset it from that of the third cylinder, so to orient the nozzle.
- figure 8 One embodiment is illustrated schematically by the figure 8.
- the common elements between figure 8 and the other figures 1 to 7 have the same reference numerals.
- the actuating assembly of Figure 8 includes a cylinder pilot 10 and two actuated cylinders 20 with a transmission device 40 mechanical between pilot cylinder and piloted cylinders. Cylinders 10, 20 and the transmission device 40 are as described above.
- a shift device 70 is interposed between the transmission 40 and each actuated cylinder 20. Only one of these devices offset 70 is shown in detail in Figure 8.
- the offset device 70 comprises a toothed crown 702 having the same axis as the rod 264 of the distributor 260 of the piloted jack corresponding. On its outer circumference, the crown 702 is in taken with the rack 420 of the transmission device 40.
- the crown 702 meshes with a satellite pinion 704 interposed between the crown 702 and a hub toothed 706 of a wheel 708 of the same axis as the rod 264 of the distributor 260.
- the pinion 704 is rotatably mounted on a rod 710 which is connected by an arm 712 to the rod 246 and forms therewith a crank, the axis of the rod 710 being parallel to that of the rod 246, but offset radially.
- the rod 246, integral in rotation with the rod 264 of the distributor is engaged with the rack 420 not only by means of a driven pinion 250, but via the pinion 704 and the crown 702.
- the wheel 708 is coupled to the output shaft 714 of a step motor at pass 716.
- a vector control computer 80 supplies the motor 716 a control signal to introduce an angular offset between the rod 246 and the rack 420 by rotation of the wheel 708 and the pinion 704. This angular offset is determined according to an orientation setpoint of nozzle given by the flight controls. Note that the very strong reduction ratio from motor input 716, in the example illustrated, allows the use of a simple stepper motor, without reducer.
- the vector controller is superimposed on the section control ejection performed by a computer 90 which receives from the pilot cylinder 10 a flap position information and supplies the hydraulic block 50 with the control signals necessary to obtain an ejection section desired by simultaneous action on the flaps by the pilot and piloted jacks.
- a dialogue link 82 is provided between the computers 70 and 80 in order to optimize the engine performance according to orientation and power instructions.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Actuator (AREA)
- Fluid-Pressure Circuits (AREA)
- Servomotors (AREA)
- Valve Device For Special Equipments (AREA)
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Abstract
Description
- un circuit hydraulique de commande,
- un vérin pilote ayant un cylindre et un piston définissant, dans le cylindre, deux chambres reliées au circuit hydraulique,
- au moins un vérin piloté ayant un cylindre et un piston définissant dans le cylindre deux chambres dont au moins une première chambre est reliée à une sortie d'un distributeur, lequel distributeur est relié au circuit hydraulique et a un organe de commande dont la position détermine la pression dans la première chambre du vérin piloté, et
- une transmission mécanique pour transmettre un déplacement du piston du vérin pilote à l'organe de commande du distributeur associé au vérin piloté, de sorte que le déplacement du piston du vérin piloté est asservi à celui du piston du vérin pilote par commande de la position de l'organe de commande du distributeur associé au vérin piloté.
- la figure 1 est une vue schématique développée d'un mode de réalisation d'un ensemble d'actionnement conforme à l'invention pour des volets de tuyère à section variable ;
- la figure 2 est une vue en coupe partielle d'un mode de réalisation d'un vérin pilote pour un ensemble d'actionnement conforme à l'invention ;
- la figure 3 est une vue à échelle agrandie d'un détail de la figure 2 ;
- la figure 4 est une vue partielle en coupe selon le plan IV-IV de la figure 3 ;
- la figure 5 est une vue en coupe partielle d'un vérin piloté de l'ensemble de la figure 1 ;
- la figure 6 est une vue à échelle agrandie d'une partie de la figure 5 ;
- la figure 7 est un schéma illustrant le principe de fonctionnement de l'ensemble de la figure 1 ; et
- la figure 8 est un schéma illustrant un mode de réalisation d'un ensemble d'actionnement conforme à l'invention pour des volets de tuyère vectorielle.
- du fait de l'existence d'une amplification hydraulique au niveau des vérins pilotés, les asservissements électriques de décalage de position sont associés aux vérins pilotés et peuvent alors être à bas niveau d'effort en puissance, et
- en cas de panne électrique dans la chaíne de commande de la tuyère, l'ensemble revient à la configuration de vérins synchronisés mécaniquement, ce qui constitue une position de repli de sécurité (tuyère non bloquée en biais).
Claims (13)
- Ensemble d'actionnement à vérins hydrauliques synchronisés, caractérisé en ce qu'il comporteun circuit hydraulique de commande (50),un vérin pilote (10) ayant un cylindre (100) et un piston (102) définissant, dans le cylindre, deux chambres reliées au circuit hydraulique,au moins un vérin piloté (20) ayant un cylindre (200) et un piston (202) définissant dans le cylindre deux chambres dont au moins une première chambre est reliée à une sortie d'un distributeur (260), lequel distributeur est relié au circuit hydraulique (50) et a un organe de commande (264) dont la position détermine la pression dans la première chambre du vérin piloté, etune transmission mécanique (40) pour transmettre un déplacement du piston (102) du vérin pilote (10) à l'organe de commande (264) du distributeur (260) associé au vérin piloté (20), de sorte que le déplacement du piston (202) du vérin piloté (20) est asservi à celui du piston du vérin pilote par commande de la position de l'organe de commande du distributeur associé au vérin pilote.
- Ensemble selon la revendication 1, caractérisé en ce que la transmission mécanique comprend un dispositif (130) de conversion du déplacement en translation du piston (102) du vérin pilote (10) en mouvement en rotation d'un pignon pilote (150), un dispositif (400) de transmission du mouvement de rotation du pignon pilote à un pignon piloté (250), et un dispositif de conversion du mouvement en rotation du pignon piloté en un déplacement en translation d'une tige de commande (264) du distributeur associé au ou à chaque vérin piloté.
- Ensemble selon la revendication 2, caractérisé en ce que le dispositif de conversion du mouvement de rotation du pignon piloté (250) en un déplacement en translation de la tige de commande (264) est formé par un premier système vis-écrou dans lequel la vis est portée par la tige de commande.
- Ensemble selon la revendication 3, caractérisé en ce qu'il comprend un deuxième système vis-écrou pour convertir un déplacement en translation du piston (202) du vérin piloté (20), agissant comme écrou en un mouvement de rotation de la vis (236) du deuxième système vis-écrou, la tige de commande (264) et la vis (236) du deuxième système vis-écrou étant vissées l'une sur l'autre de manière que les rotations de la tige de commande (264) et de la vis (236) se compensent et que la tige de commande reste immobile en translation lorsque le déplacement du piston du vérin pilote, transmis à la tige de commande, et celui du piston du vérin piloté, sont synchronisés.
- Ensemble selon l'une quelconque des revendications 2 à 4, caractérisé en ce que le ou chaque vérin piloté (20) a une première chambre (214) reliée au distributeur (260) associé à ce vérin piloté et une deuxième chambre (212) reliée en commun avec une chambre (112) du vérin pilote (10).
- Ensemble selon l'une quelconque des revendications 2 à 4, caractérisé en ce que le distributeur associé au ou à chaque vérin piloté est un distributeur double voie relié aux deux chambres du vérin piloté.
- Ensemble selon l'une quelconque des revendications 2 à 6, caractérisé en ce que le dispositif de transmission du mouvement de rotation du pignon pilote (150) à un pignon piloté (250) est constitué par un roulement linéaire souple (400) portant des crémaillères sur lesquelles engrènent les pignons.
- Ensemble selon l'une quelconque des revendications 1 à 7, dans lequel les pistons des vérins sont reliés en commun à un anneau de commande (60), caractérisé en ce que ledit ensemble comprend un vérin pilote (10) et deux vérins pilotés (20).
- Ensemble selon la revendication 8, caractérisé en ce qu'il comprend en outre au moins un vérin suiveur supplémentaire (30) alimenté par le circuit hydraulique (50) en parallèle avec le vérin pilote (10).
- Ensemble selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'il comporte un dispositif de décalage variable (70) interposé entre la transmission mécanique et l'organe de commande (264) de chaque vérin piloté (20), afin de pouvoir introduire un décalage entre une position asservie du vérin piloté (20) et une position de consigne du vérin pilote (10).
- Ensemble selon les revendications 2 et 10, caractérisé en ce que le dispositif de décalage (70) est un dispositif de décalage angulaire entre la tige de commande (264) du pignon piloté (20) et une couronne (702) en prise avec un dispositif (400) de transmission du mouvement de rotation du pignon pilote (150).
- Tuyère de turboréacteur à section d'éjection variable définie par les positions de volets mobiles, caractérisée en ce qu'elle comprend un ensemble selon l'une quelconque des revendications 1 à 9 pour l'actionnement simultané des volets mobiles.
- Tuyère de turboréacteur à section d'éjection et orientation variables, définies par les positions de volets mobiles, caractérisée en ce qu'elle comprend un ensemble selon l'une quelconque des revendications 10 et 11 pour l'actionnement des volets mobiles.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0200861 | 2002-01-24 | ||
FR0200861A FR2835021B1 (fr) | 2002-01-24 | 2002-01-24 | Ensemble d'actionnement a verins hydrauliques synchronises |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1331404A1 true EP1331404A1 (fr) | 2003-07-30 |
EP1331404B1 EP1331404B1 (fr) | 2005-03-30 |
Family
ID=8871395
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03290036A Expired - Lifetime EP1331404B1 (fr) | 2002-01-24 | 2003-01-08 | Ensemble d'actionnement à vérins hydrauliques synchronisés |
Country Status (8)
Country | Link |
---|---|
US (1) | US6837054B2 (fr) |
EP (1) | EP1331404B1 (fr) |
JP (1) | JP4098101B2 (fr) |
DE (1) | DE60300421T2 (fr) |
ES (1) | ES2237737T3 (fr) |
FR (1) | FR2835021B1 (fr) |
RU (1) | RU2311553C2 (fr) |
UA (1) | UA81742C2 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2023111484A1 (fr) * | 2021-12-17 | 2023-06-22 | Safran Electronics & Defense | Système de transmission de commande à un servo actionneur hydraulique |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7513101B2 (en) | 2005-10-28 | 2009-04-07 | Honeywell International Inc. | Synchronized motor thrust reverser actuation system |
FR2911956B1 (fr) * | 2007-01-29 | 2009-05-08 | Hispano Suiza Sa | Dispositif de mesure de la position d'un piston dans un cylindre, ensemble d'un cylindre, d'un piston et d'un tel dispositif et moteur d'aeronef comprenant un tel ensemble |
US7658059B2 (en) * | 2007-06-04 | 2010-02-09 | Crary Industries, Inc. | Synchronous drive for split sickle bars on harvester header |
FR2947870B1 (fr) * | 2009-07-09 | 2011-07-08 | Aircelle Sa | Systeme d'actionnement pour element mobile de nacelle de moteur d'aeronef, tel qu'un capot d'inverseur de poussee |
FR2958910B1 (fr) * | 2010-04-20 | 2012-04-27 | Aircelle Sa | Nacelle pour moteur d'aeronef a tuyere de section variable |
FR2974027B1 (fr) * | 2011-04-13 | 2014-09-26 | Snecma | Dispositif de compactage pour machine d'enroulement d'une texture fibreuse sur un mandrin d'impregnation |
US10412890B2 (en) * | 2015-11-10 | 2019-09-17 | Macdon Industries Ltd. | Dual sickle knife drive |
CN107314000A (zh) * | 2017-06-22 | 2017-11-03 | 马鞍山钢铁股份有限公司 | 基于连铸中间包升降液压缸同步控制系统的同步控制方法 |
EP3444483B1 (fr) * | 2017-08-17 | 2020-12-16 | Goodrich Actuation Systems Limited | Système d'actionneur hydraulique multicylindres |
US10773795B2 (en) * | 2018-09-24 | 2020-09-15 | The Boeing Company | Distributed linear hydraulic high lift actuation system with synchronization members |
CN110173487B (zh) * | 2019-05-27 | 2020-07-31 | 电子科技大学 | 一种多电液伺服执行器在切换网络下的领导同步控制方法 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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US2657539A (en) * | 1952-03-13 | 1953-11-03 | Gen Motors Corp | Synchronized power transmitter |
US2886008A (en) * | 1953-08-03 | 1959-05-12 | Gen Motors Corp | Locking actuator and valve mechanism therefor |
US3515033A (en) * | 1967-08-04 | 1970-06-02 | Gen Electric | Actuators |
FR2756329A1 (fr) | 1996-11-28 | 1998-05-29 | Snecma | Dispositif de synchronisation de verins et verin hydraulique equipe d'un dispositif de synchronisation |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4391409A (en) * | 1980-09-30 | 1983-07-05 | The Boeing Company | Positioning and control system for fan thrust reverser cowls in a turbofan engine |
US5706649A (en) * | 1995-04-03 | 1998-01-13 | Boeing North American, Inc. | Multi axis thrust vectoring for turbo fan engines |
US5609020A (en) * | 1995-05-15 | 1997-03-11 | The Boeing Company | Thrust reverser synchronization shaft lock |
US5685141A (en) * | 1995-12-26 | 1997-11-11 | General Electric Company | Lock for nozzle control in the event of hydraulic failure |
US6598386B2 (en) * | 2001-10-16 | 2003-07-29 | Honeywell International, Inc. | Jet engine thrust reverser system having torque limited synchronization |
-
2002
- 2002-01-24 FR FR0200861A patent/FR2835021B1/fr not_active Expired - Fee Related
-
2003
- 2003-01-08 ES ES03290036T patent/ES2237737T3/es not_active Expired - Lifetime
- 2003-01-08 DE DE60300421T patent/DE60300421T2/de not_active Expired - Lifetime
- 2003-01-08 EP EP03290036A patent/EP1331404B1/fr not_active Expired - Lifetime
- 2003-01-22 RU RU2003101664/06A patent/RU2311553C2/ru not_active IP Right Cessation
- 2003-01-22 JP JP2003013125A patent/JP4098101B2/ja not_active Expired - Fee Related
- 2003-01-23 US US10/349,031 patent/US6837054B2/en not_active Expired - Fee Related
- 2003-01-24 UA UA2003010649A patent/UA81742C2/uk unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2657539A (en) * | 1952-03-13 | 1953-11-03 | Gen Motors Corp | Synchronized power transmitter |
US2886008A (en) * | 1953-08-03 | 1959-05-12 | Gen Motors Corp | Locking actuator and valve mechanism therefor |
US3515033A (en) * | 1967-08-04 | 1970-06-02 | Gen Electric | Actuators |
FR2756329A1 (fr) | 1996-11-28 | 1998-05-29 | Snecma | Dispositif de synchronisation de verins et verin hydraulique equipe d'un dispositif de synchronisation |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2023111484A1 (fr) * | 2021-12-17 | 2023-06-22 | Safran Electronics & Defense | Système de transmission de commande à un servo actionneur hydraulique |
FR3130749A1 (fr) * | 2021-12-17 | 2023-06-23 | Safran Electronics & Defense | Système de transmission de commande à un servo actionneur hydraulique |
Also Published As
Publication number | Publication date |
---|---|
FR2835021A1 (fr) | 2003-07-25 |
EP1331404B1 (fr) | 2005-03-30 |
JP4098101B2 (ja) | 2008-06-11 |
DE60300421T2 (de) | 2006-03-09 |
DE60300421D1 (de) | 2005-05-04 |
JP2003269408A (ja) | 2003-09-25 |
RU2311553C2 (ru) | 2007-11-27 |
US6837054B2 (en) | 2005-01-04 |
FR2835021B1 (fr) | 2004-04-16 |
ES2237737T3 (es) | 2005-08-01 |
UA81742C2 (uk) | 2008-02-11 |
US20030136129A1 (en) | 2003-07-24 |
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