EP1972798A1 - Device for controlling the position of an actuator by a servo-valve with position memory in the event of a breakdown - Google Patents

Device for controlling the position of an actuator by a servo-valve with position memory in the event of a breakdown Download PDF

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Publication number
EP1972798A1
EP1972798A1 EP20080102832 EP08102832A EP1972798A1 EP 1972798 A1 EP1972798 A1 EP 1972798A1 EP 20080102832 EP20080102832 EP 20080102832 EP 08102832 A EP08102832 A EP 08102832A EP 1972798 A1 EP1972798 A1 EP 1972798A1
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EP
European Patent Office
Prior art keywords
actuator
bearing
cylinder
distributor
spool
Prior art date
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Granted
Application number
EP20080102832
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German (de)
French (fr)
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EP1972798B1 (en
Inventor
Pascal Marly
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Safran Aircraft Engines SAS
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Hispano Suiza SA
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Classifications

    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/002—Electrical failure
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/008—Valve failure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/862—Control during or prevention of abnormal conditions the abnormal condition being electric or electronic failure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8636—Circuit failure, e.g. valve or hose failure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8755—Emergency shut-down
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86606—Common to plural valve motor chambers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage

Definitions

  • the invention relates to controlling the position of an actuator by means of an electrically controlled servo valve.
  • a particular field of application of the invention is that of the position control of actuators used in aeronautical engines, in particular for the metering of fuel or for the adjustment of vanes of variable angle valves or flaps of valves. nozzles in gas turbine engines.
  • Servo-valves said to memory position in case of failure are well known.
  • the servovalve comprises a dispenser which, in the event of an electrical control failure, comes into a position in which dispenser utilization ports connected to control chambers of the actuator are closed. A drift from the "frozen” position of the actuator is difficult to avoid due to leakage of the hydraulic fluid contained in the control chambers.
  • the object of the invention is to provide an electrically controlled servo valve actuated device in which the position of the actuator can be frozen in the event of an electrical failure without substantial risk of drift.
  • the intermediate chamber of the actuator is connected to the high pressure and, in its safety position, the dispenser spool connects the dispenser use ports with the low pressure.
  • the locked position of the actuator slide is not influenced by leaks.
  • Low leakage of the seals does not change the value of the pressure differential that applies to the dynamic seals and thus the friction force that "freezes" the position of the actuator slide.
  • the invention is particularly applicable to a fuel flow control device in an aeronautical engine, the fuel metering actuator with an intermediate chamber connected to a high pressure fuel source and having an outlet orifice whose passage section is a function of the position of the actuator spool.
  • the dynamic seals also offer the advantage of avoiding leakage of the metered fuel flow.
  • the figure 1 schematically shows a servo valve device 10 controlling an actuator 50 forming a fuel metering device.
  • the servo valve 10 is electrically controlled and comprises an electric motor member, for example an electric torque motor 12, a hydraulic distributor 20 and associated hydro-mechanical elements (hydraulic potentiometer and mechanical counter-reaction) which form the control unit. piloting 14 of the distributor 20.
  • an electric motor member for example an electric torque motor 12, a hydraulic distributor 20 and associated hydro-mechanical elements (hydraulic potentiometer and mechanical counter-reaction) which form the control unit. piloting 14 of the distributor 20.
  • the hydraulic distributor 20 comprises a slide movable in linear translation in a cylinder.
  • the distributor 20 comprises orifices connected to a double high-pressure supply (HP) and an exhaust (or return low-pressure tarpaulin BP), use outputs U1, U2 connected to the metering device 50 and piloting inputs P1, P2 opening in control chambers located at the ends of the distributor 20.
  • the control inputs P1, P2 are connected to the control member 14, the pressures applied by it on the inputs P1, P2 acting in opposition to one of the other to control the movement of the dispenser drawer.
  • the hydraulic fluid used can be the fuel.
  • the fuel dispenser 50 comprises a slide 52 bearing two bearings 54, 56 and slidable in a cylinder 60.
  • the bearings 54, 56 share the internal volume of the cylinder 60 in two control chambers 62, 64 located at the ends of the cylinder 60 and in an intermediate chamber 66, between the bearings 54, 56.
  • the control chambers 62, 64 are connected by control lines to the use outputs U1, U2.
  • the intermediate chamber 66 is connected by a supply port 66a to the HP high pressure supply (high pressure fuel supply source) and a service port 66b to a fuel injection line.
  • HP high pressure supply high pressure fuel supply source
  • service port 66b to a fuel injection line.
  • the degree of closure of the use port 66b by the bearing 56 determines the metered flow.
  • a servo valve / fuel metering assembly as described above is known per se.
  • the hydraulic distributor spool comes into a position in which the same pressure, in this case the low pressure, is available on the operating outputs U1 and U2.
  • Each bearing 54, 56 of the dispenser 50 is then subjected, on one side to the low pressure and, on the other side, to the high pressure.
  • the tightness between the bearings 54, 56 and the cylinder 60 is achieved by means of dynamic joints producing a friction force between bearing and cylinder as a function of the difference between the pressures exerted on the two sides of each of the bearings.
  • this difference in pressure is maximum (difference between HP and BP), so the friction force is also maximum.
  • the position of the slide 52 at the time of failure can be maintained without risk of substantial drift, so that the fuel flow is frozen at its value at the moment of failure.
  • the Figures 2A and 2B show in more detail an embodiment of such a dynamic seal 70.
  • a dynamic seal 70 comprises an O-ring 72 housed in a groove 74 formed in the inner wall of the cylinder 60, and a ring 76 housed at least partly in the groove 74, bearing on the seal 72.
  • the seal 72 is an elastomer, for example Viton ® .
  • the Figure 2A shows the seal 70 when the pressures applied on both sides thereof are equal or slightly different. Under the effect of a high pressure difference between the two sides of the seal 70 ( Figure 2B ), the seal is deformed and exerts on the ring 76 a force tending to increase the force exerted on the adjacent bearing (for example the bearing 54).
  • the ring 76 is preferably made of a material with a low coefficient of friction, for example polytetrafluoroethylene (PTFE).
  • PTFE polytetrafluoroethylene
  • the housing groove of the seal could be formed in the bearing.
  • FIG. figure 3 An example of a variation of the fuel flow rate as a function of the intensity of an excitation current of the electric motor unit 12 is shown on FIG. figure 3 .
  • Operating points A, B, C, D, E and F correspond respectively to the maximum flow rate (A), the steady state (B), the limits of a minimum flow range (CD) and the limits (AB) of the "freeze" range, when the intensity of the excitation current becomes too low or zero.
  • FIGS. 4A to 4F show the positions of the slide valve 22 of the hydraulic distributor relative to the cylinder 40 of the same distributor 20 for the different operating points A to F, respectively, positions controlled by the control member 14 under the action of the electric motor member 12.
  • the drawer 22 In the position A, the drawer 22 is at a first end of its stroke in the cylinder 40, the positive difference between the pressures prevailing in the control chambers 31, 32 at the ends of the cylinder being maximum.
  • the control chambers 31, 32 are delimited by the ends of the cylinder 40 and respective bearings 23, 24 carried by the slide 22.
  • the use output U2 (which here comprises two separate bores formed in the wall of the cylinder 40) is in communication with the low pressure BP via a chamber BP 33 which is located between the bearing 23 and a bearing 25 and in which opens the exhaust port.
  • the utilization output U1 is in communication with the high pressure HP via the control chamber 31.
  • the slide 22 closes the use exit U1 by the bearing 23 and the two bores forming the utilization exit U2 by the bearing 25 and a bearing 26.
  • the drawer 22 puts the use output U2 into communication with the high pressure via an HP chamber 35 located between the bearings 24 and 26 while the use outlet 31 opens in the chamber BP 33.
  • the drawer 22 puts the BP chamber 33 in communication with the use outlet U1 and with the utilization outlet U2 via a passage 29 formed in the drawer 22 and connecting the chamber BP 33 to a chamber 34 located between the bearings 25 and 26.
  • the slide 22 is at the other end of its stroke in the cylinder 40.
  • the invention is of course applicable to hydraulic actuators other than fuel dispensers for aeronautical engines, since the position of the actuator can be "frozen” by application in two control chambers thereof a pressure (BP or HP) opposite to that prevailing in an intermediate chamber with dynamic seal between the intermediate chamber and each of the control chambers.
  • BP pressure
  • HP pressure

Abstract

The device has control chambers (62, 64) of a cylinder (60) connected with usage outlets (U1, U2) of a hydraulic distributor (20) with low pressure or high pressure. Bearings (54, 56) of a slide (52) of an actuator e.g. fuel metering valve (50), are subjected to the high and low pressures on two sides of the bearing respectively. A dynamic seal (70) assures sealing between the bearings and the cylinder, where the seal produces dynamic friction between the bearing and the cylinder based on a difference between the pressures on the sides of the bearing.

Description

Arrière-plan de l'inventionBackground of the invention

L'invention concerne la commande de position d'un actionneur au moyen d'une servo-valve à commande électrique.The invention relates to controlling the position of an actuator by means of an electrically controlled servo valve.

Un domaine particulier d'application de l'invention est celui de la commande de position d'actionneurs utilisés dans des moteurs aéronautiques, notamment pour le dosage de carburant ou pour le réglage d'aubes de distributeurs à angle de calage variable ou de volets de tuyères dans des moteurs à turbines à gaz.A particular field of application of the invention is that of the position control of actuators used in aeronautical engines, in particular for the metering of fuel or for the adjustment of vanes of variable angle valves or flaps of valves. nozzles in gas turbine engines.

Pour de telles applications, il est demandé de "geler" la position d'un organe commandé en cas de défaillance électrique au niveau de la commande de la servo-valve, pour assurer un fonctionnement de sécurité et pouvoir retrouver la position occupée avant la panne lorsque celle-ci a pu être corrigée.For such applications, it is required to "freeze" the position of a controlled member in the event of an electrical fault at the servovalve control, to ensure safe operation and to be able to regain the position occupied before the failure. when it has been corrected.

Des servo-valves dites à mémoire de position en cas de panne (ou "fail freeze") sont bien connues. On pourra en particulier se référer au document FR 2 818 331 . Dans ce document, la servo-valve comprend un distributeur qui, en cas de panne de commande électrique vient dans une position dans laquelle des orifices d'utilisation du distributeur reliés à des chambres de commande de l'actionneur sont obturés. Une dérive de la position "gelée" de l'actionneur est difficilement évitable en raison des fuites du fluide hydraulique contenu dans les chambres de commande.Servo-valves said to memory position in case of failure (or "fail freeze") are well known. In particular, reference may be made to the document FR 2,818,331 . In this document, the servovalve comprises a dispenser which, in the event of an electrical control failure, comes into a position in which dispenser utilization ports connected to control chambers of the actuator are closed. A drift from the "frozen" position of the actuator is difficult to avoid due to leakage of the hydraulic fluid contained in the control chambers.

Objet et résumé de l'inventionObject and summary of the invention

L'invention a pour but de proposer un dispositif à actionneur commandé par servo-valve commandée électriquement dans lequel la position de l'actionneur peut être gelée en cas de panne électrique sans risque substantiel de dérive.The object of the invention is to provide an electrically controlled servo valve actuated device in which the position of the actuator can be frozen in the event of an electrical failure without substantial risk of drift.

Ce but est atteint grâce à un dispositif comportant :

  • une servo-valve à commande électrique comprenant un distributeur hydraulique ayant au moins un orifice d'alimentation haute pression, au moins un orifice d'échappement à basse pression, et au moins deux orifices d'utilisation, chaque orifice d'utilisation pouvant être relié à la haute pression ou à la basse pression en fonction de la position commandée d'un tiroir du distributeur hydraulique, et
  • un actionneur comprenant un tiroir portant au moins deux paliers et pouvant coulisser dans un cylindre, l'actionneur ayant deux chambres de commande reliées à des orifices d'utilisation respectifs du distributeur de la servo-valve et situées chacune d'un côté d'un palier respectif et une chambre intermédiaire reliée à la haute ou basse pression et située entre les autres côtés des paliers,
  • le tiroir du distributeur hydraulique étant amené, en cas de panne de commande électrique, dans une position de sécurité dans laquelle il provoque l'immobilisation du tiroir de l'actionneur sensiblement dans sa position à l'instant de la panne,
    dispositif dans lequel :
  • dans la position de sécurité du tiroir du distributeur hydraulique, les chambres de commande de l'actionneur sont amenées par leur liaison avec les orifices d'utilisation du distributeur à une même pression basse ou haute opposée à celle régnant dans la chambre intermédiaire de sorte que chaque palier du tiroir de l'actionneur est alors soumis à la haute pression sur un côté et à la basse pression sur l'autre côté, et
  • l'étanchéité entre chacun desdits paliers du tiroir de l'actionneur et le cylindre de celui-ci est assurée par un joint dynamique produisant un effort de frottement entre palier et cylindre fonction de la différence entre les pressions exercées des deux côtés du palier.
This goal is achieved through a device comprising:
  • an electrically operated servo valve comprising a hydraulic distributor having at least one high pressure supply port, at least one low pressure exhaust port, and minus two use ports, each service port being connectable to high pressure or low pressure depending on the controlled position of a spool of the hydraulic distributor, and
  • an actuator comprising a slide bearing at least two bearings and slidable in a cylinder, the actuator having two control chambers connected to respective operating ports of the servo valve distributor and each located on one side of a respective bearing and an intermediate chamber connected to the high or low pressure and located between the other sides of the bearings,
  • the hydraulic distributor spool being brought, in the event of an electrical control failure, into a safety position in which it causes the immobilization of the actuator spool substantially in its position at the moment of failure,
    device in which:
  • in the safety position of the hydraulic distributor spool, the control chambers of the actuator are brought by their connection with the dispenser utilization ports at the same low or high pressure opposite to that prevailing in the intermediate chamber so that each bearing of the actuator spool is then subjected to high pressure on one side and low pressure on the other side, and
  • the seal between each of said bearings of the actuator spool and the cylinder thereof is provided by a dynamic seal producing a friction force between bearing and cylinder depending on the difference between the pressures exerted on both sides of the bearing.

Avantageusement, la chambre intermédiaire de l'actionneur est reliée à la haute pression et, dans sa position de sécurité, le tiroir du distributeur met en relation les orifices d'utilisation du distributeur avec la basse pression.Advantageously, the intermediate chamber of the actuator is connected to the high pressure and, in its safety position, the dispenser spool connects the dispenser use ports with the low pressure.

Ainsi, la position figée du tiroir de l'actionneur n'est pas influencée par des fuites. De faibles fuites des joints ne changent pas la valeur du différentiel de pression qui s'applique sur les joints dynamiques et donc l'effort de frottement qui «gèle» la position du tiroir de l'actionneur.Thus, the locked position of the actuator slide is not influenced by leaks. Low leakage of the seals does not change the value of the pressure differential that applies to the dynamic seals and thus the friction force that "freezes" the position of the actuator slide.

L'invention est notamment applicable à un dispositif de commande de débit de carburant dans un moteur aéronautique, l'actionneur formant doseur de carburant avec une chambre intermédiaire reliée à une source de carburant haute pression et ayant un orifice de sortie dont la section de passage est fonction de la position du tiroir de l'actionneur.The invention is particularly applicable to a fuel flow control device in an aeronautical engine, the fuel metering actuator with an intermediate chamber connected to a high pressure fuel source and having an outlet orifice whose passage section is a function of the position of the actuator spool.

Dans une telle application, les joints dynamiques offrent aussi l'avantage d'éviter des fuites du débit de carburant dosé.In such an application, the dynamic seals also offer the advantage of avoiding leakage of the metered fuel flow.

Brève description des dessinsBrief description of the drawings

L'invention sera mieux comprise à la lecture de la description faite ci-après, à titre indicatif mais non limitatif, en référence aux dessins annexés sur lesquels :

  • la figure 1 illustre schématiquement un dispositif à servo-valve et actionneur selon un mode de réalisation de l'invention ;
  • les figures 2A et 2B sont des vues de détail en coupe à échelle agrandie d'un type de joint dynamique utilisable pour assurer l'étanchéité entre tiroir et cylindre de l'actionneur de la figure 1,
  • la figure 3 montre une relation entre l'intensité d'un courant électrique de commande de la servo-valve et différents points de fonctionnement ; et
  • les figures 4A à 4F sont des vues montrant très schématiquement des configurations d'un distributeur hydraulique de la servo-valve de la figure 1 pour différents points de fonctionnement de la figure 3.
The invention will be better understood on reading the description given below, by way of indication but without limitation, with reference to the appended drawings in which:
  • the figure 1 schematically illustrates a servo valve and actuator device according to one embodiment of the invention;
  • the Figures 2A and 2B are detailed sectional views on an enlarged scale of a type of dynamic seal that can be used to seal between the spool and the cylinder of the actuator of the figure 1 ,
  • the figure 3 shows a relationship between the intensity of an electric control current of the servo valve and different operating points; and
  • the Figures 4A to 4F are views very schematically showing configurations of a hydraulic distributor of the servo valve of the figure 1 for different operating points of the figure 3 .

Description détaillée de modes de réalisationDetailed description of embodiments

Un mode de réalisation de l'invention sera décrit en référence aux figures 1 à 3 et 4A-4F dans le cadre de l'application au dosage (commande de débit) de carburant pour un circuit d'injection de carburant de moteur aéronautique.One embodiment of the invention will be described with reference to Figures 1 to 3 and 4A-4F as part of the application to fuel metering (flow control) for an aircraft engine fuel injection system.

La figure 1 montre schématiquement un dispositif à servo-valve 10 commandant un actionneur 50 formant doseur de carburant.The figure 1 schematically shows a servo valve device 10 controlling an actuator 50 forming a fuel metering device.

La servo-valve 10 est à commande électrique et comporte un organe moteur électrique, par exemple un moteur couple électrique 12, un distributeur hydraulique 20 et des éléments hydro-mécaniques associés (potentiomètre hydraulique et contre-réaction mécanique) qui forment l'organe de pilotage 14 du distributeur 20.The servo valve 10 is electrically controlled and comprises an electric motor member, for example an electric torque motor 12, a hydraulic distributor 20 and associated hydro-mechanical elements (hydraulic potentiometer and mechanical counter-reaction) which form the control unit. piloting 14 of the distributor 20.

Le distributeur hydraulique 20, dont un mode particulier de réalisation est décrit plus loin, comporte un tiroir mobile en translation linéaire dans un cylindre. Le distributeur 20 comprend des orifices reliés à une double alimentation haute pression (HP) et à un échappement (ou retour bâche basse pression BP), des sorties d'utilisation U1, U2 reliées au doseur 50 et des entrées de pilotage P1, P2 débouchant dans des chambres de pilotage situées aux extrémités du distributeur 20. Les entrées de pilotage P1, P2 sont reliées à l'organe de pilotage 14, les pressions appliquées par celui-ci sur les entrées P1, P2 agissant en opposition l'une de l'autre pour commander le déplacement du tiroir du distributeur. Le fluide hydraulique utilisé peut être le carburant.The hydraulic distributor 20, a particular embodiment of which is described below, comprises a slide movable in linear translation in a cylinder. The distributor 20 comprises orifices connected to a double high-pressure supply (HP) and an exhaust (or return low-pressure tarpaulin BP), use outputs U1, U2 connected to the metering device 50 and piloting inputs P1, P2 opening in control chambers located at the ends of the distributor 20. The control inputs P1, P2 are connected to the control member 14, the pressures applied by it on the inputs P1, P2 acting in opposition to one of the other to control the movement of the dispenser drawer. The hydraulic fluid used can be the fuel.

Le doseur de carburant 50 comprend un tiroir 52 portant deux paliers 54, 56 et pouvant coulisser dans un cylindre 60. Les paliers 54, 56 partagent le volume interne du cylindre 60 en deux chambres de commande 62, 64 situées aux extrémités du cylindre 60 et en une chambre intermédiaire 66, entre les paliers 54, 56. Les chambres de commande 62, 64 sont reliées par des lignes de commande aux sorties d'utilisation U1, U2.The fuel dispenser 50 comprises a slide 52 bearing two bearings 54, 56 and slidable in a cylinder 60. The bearings 54, 56 share the internal volume of the cylinder 60 in two control chambers 62, 64 located at the ends of the cylinder 60 and in an intermediate chamber 66, between the bearings 54, 56. The control chambers 62, 64 are connected by control lines to the use outputs U1, U2.

La chambre intermédiaire 66 est reliée par un orifice d'alimentation 66a à l'alimentation haute pression HP (source d'alimentation en carburant à haute pression) et par un orifice d'utilisation 66b à une conduite d'injection de carburant. Le degré d'obturation de l'orifice d'utilisation 66b par le palier 56 détermine le débit dosé.The intermediate chamber 66 is connected by a supply port 66a to the HP high pressure supply (high pressure fuel supply source) and a service port 66b to a fuel injection line. The degree of closure of the use port 66b by the bearing 56 determines the metered flow.

Un ensemble servo-valve/doseur de carburant tel que décrit ci-avant est connu en soi.A servo valve / fuel metering assembly as described above is known per se.

En cas de panne d'excitation électrique de la servo-valve, le tiroir du distributeur hydraulique vient dans une position dans laquelle une même pression, en l'espèce la basse pression, est disponible sur les sorties d'utilisation U1 et U2. Chaque palier 54, 56 du doseur 50 est alors soumis, d'un côté à la basse pression et, de l'autre côté, à la haute pression.In the event of a fault in the electrical excitation of the servo valve, the hydraulic distributor spool comes into a position in which the same pressure, in this case the low pressure, is available on the operating outputs U1 and U2. Each bearing 54, 56 of the dispenser 50 is then subjected, on one side to the low pressure and, on the other side, to the high pressure.

L'étanchéité entre les paliers 54, 56 et le cylindre 60 est réalisée au moyen de joints dynamiques produisant un effort de frottement entre palier et cylindre fonction de la différence entre les pressions exercées sur les deux côtés de chacun des paliers. Ainsi, en cas de panne d'excitation électrique de la servo-valve, cette différence de pression est maximale (différence entre HP et BP), donc l'effort de frottement est également maximal. La position du tiroir 52 au moment de la panne peut donc être conservée sans risque de dérive substantielle, de sorte que le débit de carburant est figé à sa valeur à l'instant de la panne.The tightness between the bearings 54, 56 and the cylinder 60 is achieved by means of dynamic joints producing a friction force between bearing and cylinder as a function of the difference between the pressures exerted on the two sides of each of the bearings. Thus, in the event of a failure of electrical excitation of the servo valve, this difference in pressure is maximum (difference between HP and BP), so the friction force is also maximum. The position of the slide 52 at the time of failure can be maintained without risk of substantial drift, so that the fuel flow is frozen at its value at the moment of failure.

Les figures 2A et 2B montrent de façon plus détaillée un mode de réalisation d'un tel joint dynamique 70. De façon en soi connue, celui-ci comprend un joint torique 72 logé dans une gorge 74 formée dans la paroi interne du cylindre 60, et une bague 76 logée au moins en partie dans la gorge 74, en appui sur le joint 72. Le joint 72 est en un élastomère, par exemple en Viton®. La figure 2A montre le joint 70 lorsque les pressions appliquées des deux côtés de celui-ci sont égales ou peu différentes. Sous l'effet une différence de pression élevée entre les deux côtés du joint 70 (figure 2B), le joint se déforme et exerce sur la bague 76 un effort tendant à accroître l'effort exercé sur le palier adjacent (par exemple le palier 54). La bague 76 est de préférence en un matériau à faible coefficient de friction, par exemple en polytétrafluoroéthylène (PTFE). Bien entendu, en variante, la gorge de logement du joint pourrait être formée dans le palier.The Figures 2A and 2B show in more detail an embodiment of such a dynamic seal 70. In known manner, it comprises an O-ring 72 housed in a groove 74 formed in the inner wall of the cylinder 60, and a ring 76 housed at least partly in the groove 74, bearing on the seal 72. The seal 72 is an elastomer, for example Viton ® . The Figure 2A shows the seal 70 when the pressures applied on both sides thereof are equal or slightly different. Under the effect of a high pressure difference between the two sides of the seal 70 ( Figure 2B ), the seal is deformed and exerts on the ring 76 a force tending to increase the force exerted on the adjacent bearing (for example the bearing 54). The ring 76 is preferably made of a material with a low coefficient of friction, for example polytetrafluoroethylene (PTFE). Of course, alternatively, the housing groove of the seal could be formed in the bearing.

L'utilisation des joints dynamiques permet aussi d'améliorer l'étanchéité entre les paliers 54, 56 et le cylindre 60 en fonctionnement normal du doseur, en diminuant les exigences de tolérances sur les dimensions.The use of dynamic seals also makes it possible to improve the seal between the bearings 54, 56 and the cylinder 60 during normal operation of the metering device, by reducing the requirements of dimensional tolerances.

Un exemple de variation du débit de carburant dosé en fonction de l'intensité d'un courant d'excitation de l'organe moteur électrique 12 est montré sur la figure 3.An example of a variation of the fuel flow rate as a function of the intensity of an excitation current of the electric motor unit 12 is shown on FIG. figure 3 .

Les points de fonctionnement A, B, C, D, E et F correspondent respectivement au débit maximum (A), au régime stationnaire (B), aux limites d'une plage (C-D) de débit minimum et aux limites (A-B) de la plage de "gel" de position ("fail freeze"), lorsque l'intensité du courant d'excitation devient trop faible ou nulle.Operating points A, B, C, D, E and F correspond respectively to the maximum flow rate (A), the steady state (B), the limits of a minimum flow range (CD) and the limits (AB) of the "freeze" range, when the intensity of the excitation current becomes too low or zero.

Les figures 4A à 4F montrent les positions du tiroir 22 du distributeur hydraulique par rapport au cylindre 40 de ce même distributeur 20 pour les différents points de fonctionnement A à F, respectivement, positions commandées par l'organe de pilotage 14 sous l'action de l'organe moteur électrique 12.The Figures 4A to 4F show the positions of the slide valve 22 of the hydraulic distributor relative to the cylinder 40 of the same distributor 20 for the different operating points A to F, respectively, positions controlled by the control member 14 under the action of the electric motor member 12.

Dans la position A, le tiroir 22 se trouve à une première extrémité de sa course dans le cylindre 40, la différence positive entre les pressions régnant dans les chambres de pilotage 31, 32 aux extrémités du cylindre étant maximale. Les chambres de pilotage 31, 32 sont délimitées par les extrémités du cylindre 40 et des paliers respectifs 23, 24 portés par le tiroir 22. La sortie d'utilisation U2 (qui comprend ici deux perçages distincts formés dans la paroi du cylindre 40) est en communication avec la basse pression BP via une chambre BP 33 qui est située entre le palier 23 et un palier 25 et dans laquelle s'ouvre l'orifice d'échappement. La sortie d'utilisation U1 est en communication avec la haute pression HP via la chambre de pilotage 31.In the position A, the drawer 22 is at a first end of its stroke in the cylinder 40, the positive difference between the pressures prevailing in the control chambers 31, 32 at the ends of the cylinder being maximum. The control chambers 31, 32 are delimited by the ends of the cylinder 40 and respective bearings 23, 24 carried by the slide 22. The use output U2 (which here comprises two separate bores formed in the wall of the cylinder 40) is in communication with the low pressure BP via a chamber BP 33 which is located between the bearing 23 and a bearing 25 and in which opens the exhaust port. The utilization output U1 is in communication with the high pressure HP via the control chamber 31.

Dans la position B, le tiroir 22 obture la sortie d'utilisation U1 par le palier 23 et les deux perçages formant la sortie d'utilisation U2 par le palier 25 et un palier 26.In the position B, the slide 22 closes the use exit U1 by the bearing 23 and the two bores forming the utilization exit U2 by the bearing 25 and a bearing 26.

Dans les positions C et D, le tiroir 22 met en communication la sortie d'utilisation U2 avec la haute pression via une chambre HP 35 située entre les paliers 24 et 26 tandis que la sortie d'utilisation 31 s'ouvre dans la chambre BP 33.In positions C and D, the drawer 22 puts the use output U2 into communication with the high pressure via an HP chamber 35 located between the bearings 24 and 26 while the use outlet 31 opens in the chamber BP 33.

Dans les positions E et F, le tiroir 22 met en communication la chambre BP 33 avec la sortie d'utilisation U1 et avec la sortie d'utilisation U2 via un passage 29 formé dans le tiroir 22 et reliant la chambre BP 33 à une chambre 34 située entre les paliers 25 et 26. Dans la position F, le tiroir 22 se trouve à l'autre extrémité de sa course dans le cylindre 40.In the positions E and F, the drawer 22 puts the BP chamber 33 in communication with the use outlet U1 and with the utilization outlet U2 via a passage 29 formed in the drawer 22 and connecting the chamber BP 33 to a chamber 34 located between the bearings 25 and 26. In the position F, the slide 22 is at the other end of its stroke in the cylinder 40.

Bien entendu, le profil de fonctionnement de la figure 3 et l'agencement interne du distributeur de la servo-valve décrits ci-avant sont donnés simplement à titre d'exemple, d'autres formes étant possibles dès lors qu'en cas de panne d'excitation électrique de la servo-valve 10 le tiroir du distributeur hydraulique 20 vient dans une position de sécurité dans laquelle, dans le cas présent, les sorties d'utilisation U1 et U2 sont toutes deux à la basse pression pour assurer le "gel" de la position du doseur 50.Of course, the operating profile of the figure 3 and the internal arrangement of the distributor of the servo-valve described above are given merely by way of example, other forms being possible since in the event of failure of electrical excitation of the servo valve 10 the Hydraulic distributor slide 20 comes into a safety position in which, in this case, the use outlets U1 and U2 are both at low pressure to "freeze" the position of the metering device 50.

L'invention est bien entendu applicable à des actionneurs hydrauliques autres que des doseurs de carburant pour moteurs aéronautiques, dès lors que la position de l'actionneur peut être "gelée" par application dans deux chambres de commande de celui-ci d'une pression (BP ou HP) opposée à celle régnant dans une chambre intermédiaire avec étanchéité par joints dynamiques entre la chambre intermédiaire et chacune des chambres de commande.The invention is of course applicable to hydraulic actuators other than fuel dispensers for aeronautical engines, since the position of the actuator can be "frozen" by application in two control chambers thereof a pressure (BP or HP) opposite to that prevailing in an intermediate chamber with dynamic seal between the intermediate chamber and each of the control chambers.

Claims (4)

Dispositif de commande de position d'un actionneur comportant : - une servo-valve (10) à commande électrique comprenant un distributeur hydraulique (20) ayant au moins un orifice d'alimentation haute pression (HP), au moins un orifice d'échappement à basse pression (BP), et au moins deux orifices d'utilisation (U1, U2), chaque orifice d'utilisation pouvant être relié à la haute pression ou à la basse pression en fonction de la position commandée d'un tiroir du distributeur hydraulique, et - un actionneur (50) comprenant un tiroir (52) portant au moins deux paliers (54, 56) et pouvant coulisser dans un cylindre (60), l'actionneur ayant deux chambres de commande (62, 64) reliées à des orifices d'utilisation respectifs (U1, U2) du distributeur de la servo-valve et situées chacune d'un côté d'un palier respectif et une chambre intermédiaire (66) reliée à la haute ou basse pression et située entre les autres côtés des paliers, - le tiroir (22) du distributeur hydraulique étant amené, en cas de panne de commande électrique, dans une position de sécurité dans laquelle il provoque l'immobilisation du tiroir de l'actionneur sensiblement dans sa position à l'instant de la panne,
caractérisé en ce que : - dans la position de sécurité du tiroir (22) du distributeur hydraulique, les chambres de commande (62, 64) de l'actionneur sont amenées par leur liaison avec les orifices d'utilisation (U1, U2) du distributeur à une même pression basse ou haute opposée à celle régnant dans la chambre intermédiaire (66) de sorte que chaque palier (54, 56) du tiroir de l'actionneur est alors soumis à la haute pression sur un côté et à la basse pression sur l'autre côté, et - l'étanchéité entre chacun desdits paliers (54, 56) du tiroir de l'actionneur et le cylindre (60) de celui-ci est assurée par un joint dynamique (70) produisant un effort de frottement entre palier et cylindre fonction de la différence entre les pressions exercées des deux côtés du palier. An actuator position control device comprising: an electrically operated servo valve (10) comprising a hydraulic distributor (20) having at least one high pressure supply port (HP), at least one low pressure exhaust port (LP), and at least two use ports (U1, U2), each service port being connectable to high pressure or low pressure depending on the controlled position of a hydraulic distributor spool, and an actuator (50) comprising a slide (52) bearing at least two bearings (54, 56) and being slidable in a cylinder (60), the actuator having two control chambers (62, 64) connected to respective use (U1, U2) of the servo valve manifold and each located on one side of a respective bearing and an intermediate chamber (66) connected to the high or low pressure and located between the other sides of the bearings, - the drawer (22) of the hydraulic distributor being brought, in the event of failure of the electrical control, in a safety position in which it causes the immobilization of the actuator drawer substantially in its position at the moment of failure,
characterized in that - In the safety position of the spool (22) of the hydraulic distributor, the control chambers (62, 64) of the actuator are brought by their connection with the use orifices (U1, U2) of the distributor at the same pressure low or high opposite to that in the intermediate chamber (66) so that each bearing (54, 56) of the actuator spool is then subjected to high pressure on one side and low pressure on the other side , and - the seal between each of said bearings (54, 56) of the actuator spool and the cylinder (60) thereof is provided by a dynamic seal (70) producing a friction force between bearing and cylinder depending on the difference between the pressures exerted on both sides of the landing. Dispositif selon la revendication 1, caractérisé en ce que la chambre intermédiaire (66) de l'actionneur est reliée à la haute pression (HP) et, dans sa position de sécurité, le tiroir du distributeur (20) met en relation les orifices d'utilisation (U1, U2) du distributeur avec la basse pression (BP).Device according to claim 1, characterized in that the intermediate chamber (66) of the actuator is connected to the high pressure (HP) and, in its safety position, the slide of the distributor (20) connects the orifices of the use (U1, U2) of the distributor with the low pressure (BP). Dispositif de commande de débit de carburant dans un moteur aéronautique, comprenant un dispositif de commande de position selon l'une quelconque des revendications 1 et 2 dans lequel l'actionneur (50) forme doseur de carburant, la chambre intermédiaire (66) étant reliée à une source de carburant haute pression et ayant un orifice de sortie dont la section de passage est fonction de la position du tiroir de l'actionneur.A fuel flow control device in an aeronautical engine, comprising a position control device according to any one of claims 1 and 2 wherein the actuator (50) forms a fuel metering device, the intermediate chamber (66) being connected to a high pressure fuel source and having an outlet whose passage section is a function of the position of the actuator spool. Moteur aéronautique comprenant un dispositif de commande selon l'une quelconque des revendications 1 à 3.Aeronautical engine comprising a control device according to any one of claims 1 to 3.
EP20080102832 2007-03-21 2008-03-20 Device for controlling the position of an actuator by a servo-valve with position memory in the event of a breakdown Active EP1972798B1 (en)

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FR0753960A FR2914030B1 (en) 2007-03-21 2007-03-21 DEVICE FOR CONTROLLING THE POSITION OF AN ACTUATOR BY SERVOVALVE WITH POSITION MEMORY IN CASE OF FAILURE

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KR102094425B1 (en) 2013-01-31 2020-03-31 파커-한니핀 코포레이션 Direction control valve with metering notches on the spool for reduced flow in the open end position
US11242875B2 (en) 2020-03-05 2022-02-08 Honeywell International Inc. System that maintains the last commanded position of device controlled by a two-stage, four-way electrohydraulic servo valve upon power interruption

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BRPI0800652B1 (en) 2019-06-25
DE602008000352D1 (en) 2010-01-21
CA2626724C (en) 2014-10-07
IL190313A0 (en) 2009-09-22
MA31718B1 (en) 2010-10-01
ZA200802613B (en) 2009-08-26
UA95080C2 (en) 2011-07-11
BRPI0800652A2 (en) 2011-04-19
JP5058857B2 (en) 2012-10-24
RU2459124C2 (en) 2012-08-20
SG165346A1 (en) 2010-10-28
FR2914030B1 (en) 2009-07-03
ES2336972T3 (en) 2010-04-19
US8091584B2 (en) 2012-01-10
CA2626724A1 (en) 2008-09-21
RU2008110813A (en) 2009-09-27
US20080230127A1 (en) 2008-09-25
SG146572A1 (en) 2008-10-30
MX2008003800A (en) 2009-02-27
JP2008241039A (en) 2008-10-09
EP1972798B1 (en) 2009-12-09
CN101270768A (en) 2008-09-24
ATE451556T1 (en) 2009-12-15
IL190313A (en) 2011-06-30
FR2914030A1 (en) 2008-09-26
CN101270768B (en) 2012-03-28

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