• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Hydraulic servovalve (1) comprising: - a power stage (3) comprising a power distribution member for putting into communication one or more service ports (C1, C2) with a supply port (P) in hydraulic fluid and a return port (R); a driving stage (4) for controlling the position of the power distribution member, the driving stage (4) comprising a controllable torque motor (MC) for actuating a fluid ejection member integral with a elastically deformable element adapted to vary a pilot pressure of the power distribution member; characterized in that the fluid ejection member comprises a first and a second fluid injector (60, 63) supplied by fluid supply means adapted to feed either one of the first and second fluid injectors ( 60, 63), or both injectors simultaneously.
    公开号:FR3024505A1
    申请号:FR1457473
    申请日:2014-07-31
    公开日:2016-02-05
    发明作者:Jean-Luc Bertrand
    申请人:Zodiac Hydraulics SAS；
    IPC主号:
    专利说明:

    [0001] Field of the Invention The invention relates to a hydraulic servovalve with jet deflection. STATE OF THE ART A conventional jet deflection servovalve comprises a control stage and a power stage. The power stage generally comprises a movable power distribution member in a housing of the servovalve body between two extreme positions for communicating one or more service ports with a hydraulic pressure servovalve power port. and a return port. The displacement of the power distribution member in its housing makes it possible to deliver an output pressure or a flow rate proportional to the displacement of said power distribution member. The drive stage of such a servovalve comprises a torque motor whose rotor is connected to a mobile hydraulic injector facing a fixed hydraulic receiver. Generally, the torque motor of the control stage acts on magnetic vanes of a movable assembly of which an elastically deformable element is functionally connected to a fluid supply duct provided at its end with the hydraulic injector. The magnetic beads are integral with the elastically deformable element so as to cause a deformation of this element proportional to the value of the electrical setpoint. This deformation causes a displacement of the injector vis-à-vis the fixed receiver and generates a pilot pressure that results from the difference in pressures transmitted by drilled channels at the ends of the housing of the power distribution member. This pilot pressure is used to finely move the power member.
    [0002] There are conventionally three types of movable assembly of a driving stage of a jet deflection servovalve: a first type in which the elastically deformable element is a bar subjected to torsion; a second type in which the elastically deformable element is a tube subjected to bending; a third type in which the elastically deformable element is a tube subjected to torsion. This third type was the subject of a patent application FR2963393 by the applicant. These servovalves also include a feedback member which slaves the position of the power distribution member to the rotor of the torque motor and generates on the torque motor a torque which is withdrawn from the control action. The feedback member may be of the mechanical type, using a feedback rod connecting the rotor of the servovalve to the power distribution member. The feedback device may also comprise a position sensor, of Linear Variable Differential Transformer (LVDT) type, measuring the position of the power unit and whose instructions are transmitted to a processing unit controlling the electrical setpoint received by the controller. pilot stage. The passage sections of the hydraulic fluid supply duct and the hydraulic injector are sized to permit a laminar flow of fluid and a flow rate sufficient to rapidly displace the power distribution member while minimizing flow. taken for the operation of the servovalve. Indeed, a too small diameter of the conduit and / or the injector leads to insufficient flow at the injector outlet and degrades the reactivity of the servovalve. Conversely, a large diameter increases the constant consumption of the servovalve and therefore the energy demand of the hydraulic system. The sizing of the fluid passage sections is generally based on a hydraulic fluid behavior corresponding in particular to ranges of temperature, pressure and viscosity defined according to the operating conditions of the equipment. However, there are use situations in which these parameters may take values outside the sizing ranges. A particularly critical situation concerns the cold start. As the viscosity of hydraulic fluids varies with temperature, this viscosity may reach values that are incompatible with servovalve operation, including in a degraded mode. To address this problem, hydraulic fluid reheating devices have been envisaged using electric tracing devices which bring the hydraulic fluid to a temperature permitting operation of the servovalve. This solution complicates and increases the installation on which the servovalve is mounted, which is particularly detrimental in aeronautical applications. In addition, it is necessary to wait for the fluid to reach the required temperature before being able to use the device, which poses availability problems, for example in military or civil applications in which the equipment must be able to be operational in a machine. reduced time or in extreme weather conditions. It has also been envisaged to improve the low temperature viscosity of the hydraulic fluid, but fluids with good low temperature behavior have a limited maximum use temperature, and vice versa. OBJECT OF THE INVENTION An object of the invention is to reduce the operations prior to the commissioning of a servovalve at low temperature. SUMMARY OF THE INVENTION To this end, there is provided a hydraulic servo valve comprising: a power stage comprising a power distribution member movable between two extreme positions for placing one or more service ports in communication with a port of hydraulic fluid supply and a return port; a control stage for controlling the position of the power distribution member, the control stage comprising a controllable torque motor for actuating a fluid ejection member integral with an elastically deformable element and adapted to vary a pilot pressure of the power distribution member. According to the invention, the fluid ejection member comprises a first and a second fluid injector fed by fluid supply means adapted to feed either one of the first and second fluid injector, or the two injectors. simultaneously. According to a particular embodiment, the first and second injector of the servovalve are respectively fed by a first and a second fluid supply line having different passage sections and / or whose passage sections of the injectors are different. According to the applications, the elastically deformable element is a torsion bar, a bending tube or a torsion tube. Ideally, the movable element comprises a feedback rod intended to cooperate with the power distribution member of the power stage.
    [0003] Preferably, the power stage comprises a power distribution member displaceable in a tubular housing and each end of the tubular housing comprises a chamber into which a first fluid inlet opens, bringing the fluid ejected by the first fluid injector and a second inlet of fluid bringing the fluid ejected by the second fluid injector. BRIEF DESCRIPTION OF THE DRAWINGS Reference will be made to the appended figures, in which: FIG. 1 is a diagrammatic representation of a first embodiment of a servovalve according to the invention; Figure 2 is a schematic perspective view of a moving assembly according to the invention; Figure 3 is a schematic view of an equipment comprising a servovalve according to the invention; Figure 4 is a schematic vertical sectional view of a second embodiment of the servovalve according to the invention; Figure 5 is a schematic vertical sectional view of a third embodiment of the servovalve according to the invention; Figure 6 is a schematic vertical sectional view of a fourth embodiment of the servovalve according to the invention. DETAILED DESCRIPTION OF THE INVENTION With reference to FIG. 1, the servovalve according to the invention, generally designated 1, comprises in a body 2 a power stage 3 and a control stage 4. The power stage 3 comprises an element The power distribution member 5 is slidably mounted in a tubular housing 6 of the body 2. The power distribution member 5 is arranged, in known manner, to selectively connect the housing slots 6 fluidly connected to the ports P d. supply of hydraulic fluid as well as the service ports C1, C2 and return R of the servovalve. The ends of the power distribution member 5 define respectively with the ends 7 and 8 of the tubular housing 6 a first chamber 9 and a second chamber 10. Two fluid inlets 11 and 12 open into the first chamber 9 of the housing tubular 6 while two other fluid inlets 13 and 14 open into the second chamber 10 of the tubular housing 6. The fluid inlets thus open into separate chambers. The fluid inlets 11 and 13 are respectively connected to the first reception port 15 and the second reception port 16 of a first fluid receiver 17 of the control stage 4. The fluid inlets 12 and 14 are in turn respectively connected to the first receiving port 18 and the second receiving port 19 of a second fluid receiver 20 of the control stage 4 .. The power distribution member is movable between a first and a second extreme position corresponding respectively at a minimum volume and a maximum volume of the first chamber 9.
    [0004] With reference to FIGS. 1 and 2, the piloting stage 4 comprises a torque motor MC whose coils 21 magnetically interact with the ends of a rectangular magnetic pallet 51 of a moving assembly 50 in order to control its position. according to an electrical instruction. The movable assembly 50 also comprises a central element 52 of substantially rectangular shape and whose longitudinal direction extends substantially perpendicularly to the magnetic pallet 51. The first end 52.1 of the central element 52 is connected via a first bar of torsion 53 to a first support 54 in the form of a half disc and provided with two bores intended to receive fastening screws 55 of the first support 54 on the body 2 of the servovalve 1. The second end 52.2 of the central element 52 is re linked via a second torsion bar 56 to a second support 57 in the form of a half-disc and provided with two bores intended to receive fastening screws 55 of the second support 57 on the body 2 of the servovalve 1. The first support 54 comprises a third bore 58 through which extends a first pipe 59 of an internal diameter of the order of one millimeter (corresponding to a passage section of 0. 8 mm2) and which makes a 180 ° arc and then extends through the first end 52.1 of the central element 52. The pipe 59 is connected to the support 54 and the first end 52.1 of the element central 52, for example by welding. The first end 59.1 of the portion of the first pipe 59 connected to the support 54 is supplied with hydraulic fluid at the supply pressure via the housing 6 while the second end 59.2 of the portion of the first pipe 59 connected to the element central 52 is connected to a first fluid injector 60 whose diameter is between 2 and 4 tenths of a millimeter and which faces the first fluid receiver 17. The second end 59.2 of the first conduit 59 also comprises a feedback rod 70 cooperating with a groove 71 of the power distribution member 5. In a symmetrical manner, the second support 57 comprises a third bore 61 through which extends a second pipe 62 having a diameter of between two and three millimeters and which realizes a 180 ° arc and then extends through the second end 52.2 of the central element 52. The first end 62.1 d e the portion of the second pipe 62 connected to the support 57 and the second end 62.2 of the portion of the second pipe 62 connected to the central element 52 are respectively connected to the support 57 and the second end 52.2 of the central element 52 for example by welding. The first end 62.1 of the second pipe 62 is supplied with hydraulic fluid at the supply pressure via the housing 6. A hydraulic distributor 80 is installed on the fluid supply of the first end 62.1 of the second conduit 62. second end 62.2 is, in turn, provided with a second fluid injector 63, whose diameter is of the order of one millimeter, facing the second fluid receiver 20. The distributor 80 is electrically controlled using an electrical coil 81 and is brought back into position by a spring 82. The distributor 80 can adopt two states. A first state connecting the fluid supply of the end 62.1 of the second conduit 62 to the housing 6 and allowing its supply of fluid to the supply pressure, and a second state (shown in Figure 1) in which the supply of fluid from the end 62.1 of the second conduit 62 is connected to the return port R of the servovalve. A two-stage servovalve 1 is thus obtained, comprising a power stage 3 comprising a power distribution member 5 movable between two extreme positions for putting the service ports C1 and C2 into communication with a fluid supply port P. The servovalve 1 also comprises a control stage 4 comprising a controllable torque motor MC for controlling the position of the movable assembly 50 of which an elastically deformable element composed of the bars 53 and 56 is integral with the hydraulic fluid injectors 60 and 63 via the central element 52. The modification of the position of the fluid injectors 60 and 63 vis-à-vis the fluid receivers 17 and 20 varies the pressures in the chambers 9 and 10 and results in a control pressure of the power distribution member 5 which moves it in the housing 6. The injectors 60 and 63 fluid can operate simultaneously and the power supply The insertion of the second fluid injector 63 can be interrupted by applying an electrical command to the coil 81 controlling the change of state of the distributor 80 and allowing the operation of the single fluid injector 60.
    [0005] Such a servovalve 1 is advantageously used to control a hydraulic actuator 90 of a device 91, such as an aircraft. In the case of a commissioning of the equipment 91 incorporating the servovalve 1 by very low temperature, the viscosity of the hydraulic fluid circulated by the pump 92 in the hydraulic network 93 of the equipment 91 is particularly high. The distributor 80 is then placed in its first position and supplies hydraulic fluid to the first ends 62.1 and 59.1 of the lines 62. In this situation, the two fluid injectors 60 and 63 operate simultaneously. When an electrical setpoint is applied to the torque motor MC, the magnetic field thus created moves the magnetic paddle 51 and causes a displacement of the first fluid injector 60 and the second injector 63 respectively relative to the fluid injectors 17 and 20. In FIG. 2, the pallet 51 has been displaced in the direction 94, thus causing the fluid injectors 60 and 63 to move in a direction 95 and 96 respectively. The displacements in the directions 95 and 96 respectively In a first embodiment, fluid injectors 17 and 20 supply a large quantity of hydraulic fluid to the first fluid receivers 15 and 18. The first fluid inlets 11 and 12, respectively, of the first fluid receivers 15 and 18 open into the first chamber 9 and there bring the hydraulic fluid. The amount of hydraulic fluid supplied to the first chamber 9 increases the pressure therein relative to the pressure in the chamber 10. This pressure differential then moves the power distribution member 5 of the chamber 9 to the chamber 10 and then discovers the slots of the housing 6 so as to deliver pressure to the service ports C1 and C2 proportional to the electrical setpoint applied to the torque motor MC. While a hydraulic fluid supply by a single conduit 59 would not have allowed the creation of a pressure differential sufficient to move the power member 5 due to the high viscosity of the low temperature hydraulic fluid, the combined supply of hydraulic fluid via the ducts 59 and 62 makes it possible, at low temperature, to use the servovalve 1 for commissioning the equipment 90. When the hydraulic fluid reaches a temperature, and therefore a viscosity, corresponding to the nominal operating conditions of the hydraulic fluid in the servovalve 1, an electrical setpoint is sent to the coil 81 so as to pass the hydraulic spool 80 in its second position and interrupt the fluid supply of the second fluid injector 63, and therefore its operation.
    [0006] A servovalve 1 is thus obtained which, for a limited excess weight corresponding substantially to the mass of the second duct 62, almost immediately brings into service a servovalve at a low temperature. Elements identical or similar to those previously described will have a reference identical thereto in the description which follows of the second, third and fourth embodiments. With reference to FIG. 4, the control stage 2 of the servovalve 50 comprises a magnetic paddle 51 mounted at a first end of a torsion tube 100. The second end 101 of the torsion tube 100 comprises a first pipe 59 and a second fluid supply pipe 62 respectively for the hydraulic injectors 60 and 63. The fluid injectors 60 and 63 are integral with the torsion tube 100 and face respectively receivers 17 and 20 whose fluid receivers 15, 16, 18 and 19 are connected to the chambers 9 and 10 of the housing 6. In use, an electrical instruction applied to the magnetic pallet 51 causes a twisting of the tube 100 about its axis. This torsion causes the injectors 60 and 63 to move relative to the receivers 17 and 20. The supply of hydraulic fluid via the ducts 11 to 14 connected to the fluid receivers 15 to 19 generates a pilot pressure which displaces the fluid. power distribution member 5 so as to deliver an output pressure to the ports C1 and C2 proportional to the electrical setpoint applied to the magnetic pallet 51. When the hydraulic fluid reaches a temperature, and therefore a viscosity, corresponding to the conditions of nominal operation of the hydraulic fluid in the servovalve 1, an electrical setpoint is sent to the coil 81 so as to pass the hydraulic spool 80 in its second position and interrupt the fluid supply of the second fluid injector 63, and therefore its operation . With reference to FIG. 5, the third embodiment of the hydraulic servovalve 50 is described. According to this embodiment, the first chamber 9 comprises a cylinder 30 movable in the tubular housing 6 defining a permanent under-chamber 31 and a transient piloting chamber 32. The sub-control chamber 31 is defined firstly by the end 7 of the tubular housing 6 and secondly by a first face 33 of the cylinder 30. The second face 34 of the cylinder 30 opposite the first face 33 is curved and is in contact with one end 35 of the power distribution 5. The transient piloting chamber 32 is defined on the one hand by the second face 34 of the cylinder 30 and on the other hand by the end 35 of the power unit 5. The fluid inlet 11 It opens into the permanent under-cockpit 31 while the fluid inlet 12 opens into the transient piloting chamber 32. The second chamber 10 of the tubular housing 6 comprises, in a homologous manner, a sub-piloting chamber. Germanent 36 separated from a transient piloting chamber 37 by a cylinder 38 identical to the cylinder 30. The fluid inlet 13 opens into the permanent pilot chamber 36 while the fluid inlet 14 opens into the sub chamber of transient control 37. The operation of the servovalve remains identical to that previously described. This configuration allows summation of the forces exerted by the pressurization of each of the sub-chambers.
    [0007] The fourth embodiment described with reference to FIG. 6 is an improvement of the third embodiment of FIG. 5. In this embodiment, a hydraulic drawer distributor 83 receives branches 84 and 85 respectively from the The dispenser 83 is electrically controlled by means of an electric coil 86 and is brought back into position by a spring 87. The dispenser 83 can adopt two or more fluid conduits 12 and 14 which supply the transient piloting chambers 32 and 37. states. A first state in which the leads 84 and 85 are plugged, and a second state (shown in Figure 6) in which these leads 84 and 85 are connected to the return port R of the servovalve. The first state of the dispenser 83 is adopted when the dispenser 80 is in its first state. In this configuration, the second fluid injector 63 is energized and the leads 84 and 85 are plugged. When the distributor 80 goes into its second state and cuts off the fluid supply of the second fluid injector 63, the distributor 83 also passes into its second state. In this configuration, the two transient piloting chambers 32 and 37 are equipressed. This reduces parasitic forces on the movable power member 5 from the recirculation of the fluid between the transient control chambers 32 and 37. Preferably, the electrical coils 81 and 86 for controlling the hydraulic drawers 80 and 83 can be coupled. Of course, the invention is not limited to the embodiments described but encompasses any variant within the scope of the invention as defined by the claims. In particular, although here the power distribution member is slidably mounted in a tubular housing of the servovalve body, the invention is also applicable to other types of mounting of the actuator member. power in the body of the servovalve such as a mounting in a sleeve reported in the body of the servovalve; although here, a feedback rod is operatively connected to the power distribution member, the invention applies to other types of feedback means such as a feedback including an LVDT measuring the position of the power unit and whose information is used to modulate the electrical setpoint applied to the control stage; - Although here the movable assembly comprises two elastic elements in the form of two torsion bars, the invention is also applicable to other types of elastically deformable element such as, for example, a single torsion bar a torsion tube or a bending tube; although here the passage sections of the first and second fluid supply lines are different, the invention also applies to first and second fluid supply lines of identical passage section; although here the passage sections of the first and second fluid injector are different, the invention also applies to first and second fluid injectors of identical passage section; although here the servovalve comprises two service ports, the invention also applies to a servovalve having a number of different service ports, such as a single service port or more than two; although here the control stage is included in the body of the servovalve, it can be fixed in part or totally on the body of the servovalve and not contained therein; -Although here the supports of the central elements for fixing the movable assembly on the body of the servo valve are in the form of a half disc, the invention also applies to other means of fixing the moving assembly to the body of the servovalve such as square or any shape supports, or attachment to intermediate parts attached to the body of the servovalve; although here the distributor is electrically controlled by means of an electric coil, the invention also applies to other types of distributor control actuator or other means of changing the state of the distributor as for example a change of state induced by pressure or with a mechanical control by thermal effect; although here the diameters of the first and second conduits are respectively one millimeter and two to three millimeters, the invention also applies to other values of pipe diameters, or even pipes of equal diameter, it is similarly for the diameters of the injectors; although here the faces of the cylinders in contact with the ends of the power distribution member are curved, the invention is also applicable to other geometries of contact faces such as flat faces, concave or any.
    权利要求:
    Claims (8)
    [0001]
    REVENDICATIONS1. Hydraulic servovalve (1) comprising: - a power stage (3) comprising a power distribution member movable between two extreme positions for placing one or more service ports (C1, C2) in communication with a power supply port (P ) hydraulic fluid and a return port (R); a driving stage (4) for controlling the position of the power distribution member, the driving stage (4) comprising a controllable torque motor (MC) for actuating a solid-state fluid ejection member; an elastically deformable element adapted to vary a driving pressure of the power distribution member; characterized in that the fluid ejection member comprises a first and a second fluid injector (60, 63) supplied by fluid supply means adapted to feed either one of the first and second fluid injectors ( 60, 63), or both injectors simultaneously.
    [0002]
    2. A servovalve (1) according to claim 1 wherein the first and second fluid injector (60, 63) are respectively fed by a first and a second fluid supply line (59, 62) having passage sections. different fluids.
    [0003]
    The servovalve (1) according to claim 1 wherein the first and second hydraulic fluid injectors (60, 63) have different fluid passage sections.
    [0004]
    4. Servovalve (1) according to claim 1 wherein the elastically deformable element (53, 56) is a torsion bar.
    [0005]
    5. Servovalve (1) according to claim 1 wherein the elastically deformable element is a flexure tubede.
    [0006]
    6. Servovalve (1) according to claim 1 wherein the elastically deformable element is a torsion tube.
    [0007]
    7. Servovalve (1) according to claim 1, wherein the movable member (50) comprises a feedback rod (70) intended to cooperate with the power distribution member (5) of the power stage (3). ).
    [0008]
    8. Servovalve (1) according to claim 1 wherein, the power stage (3) comprising a power distribution member (5) movable in a tubular housing (6), each end (7, 8) of the tubular housing (6) comprises a chamber (9, 10) into which a first hydraulic fluid inlet (12, 14) conveys the hydraulic fluid ejected by the first fluid injector (60) and a second hydraulic fluid inlet (11). , 13) bringing the hydraulic fluid ejected by the second fluid injector (63).
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    同族专利:
    公开号 | 公开日
    US9677682B2|2017-06-13|
    FR3024505B1|2016-08-05|
    US20160033052A1|2016-02-04|
    ES2617348T3|2017-06-16|
    EP2980417B1|2017-01-11|
    EP2980417A1|2016-02-03|
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    法律状态:
    2015-06-26| PLFP| Fee payment|Year of fee payment: 2 |
    2016-02-05| PLSC| Search report ready|Effective date: 20160205 |
    2016-07-21| PLFP| Fee payment|Year of fee payment: 3 |
    2017-07-24| PLFP| Fee payment|Year of fee payment: 4 |
    2018-07-25| PLFP| Fee payment|Year of fee payment: 5 |
    2020-06-23| PLFP| Fee payment|Year of fee payment: 7 |
    2021-04-16| CD| Change of name or company name|Owner name: SAFRAN AEROSYSTEMS HYDRAULICS, FR Effective date: 20210308 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1457473A|FR3024505B1|2014-07-31|2014-07-31|SERVOVALVE WITH DOUBLE MOBILE ASSEMBLY|FR1457473A| FR3024505B1|2014-07-31|2014-07-31|SERVOVALVE WITH DOUBLE MOBILE ASSEMBLY|
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    ES15174703.7T| ES2617348T3|2014-07-31|2015-06-30|Double mobile mounting valve servo|
    US14/794,141| US9677682B2|2014-07-31|2015-07-08|Servo valve with double mobile assembly|
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