EP2443332B1 - Vanne comportant un dispositif de transformation de mouvement - Google Patents

Vanne comportant un dispositif de transformation de mouvement Download PDF

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Publication number
EP2443332B1
EP2443332B1 EP10726947.4A EP10726947A EP2443332B1 EP 2443332 B1 EP2443332 B1 EP 2443332B1 EP 10726947 A EP10726947 A EP 10726947A EP 2443332 B1 EP2443332 B1 EP 2443332B1
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EP
European Patent Office
Prior art keywords
valve
valve according
tubular wall
shutter
motor
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.)
Active
Application number
EP10726947.4A
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German (de)
English (en)
French (fr)
Other versions
EP2443332A1 (fr
Inventor
Laurent Albert
Gabriel Ridolfi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Systemes de Controle Moteur SAS
Original Assignee
Valeo Systemes de Controle Moteur SAS
Priority date (The priority date 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 date listed.)
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Publication of EP2443332A1 publication Critical patent/EP2443332A1/fr
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Publication of EP2443332B1 publication Critical patent/EP2443332B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/12—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having slidably-mounted valve members; having valve members movable longitudinally of conduit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/04—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by mechanical control linkages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
    • F02D11/10—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
    • F02D11/10—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type
    • F02D11/105—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type characterised by the function converting demand to actuation, e.g. a map indicating relations between an accelerator pedal position and throttle valve opening or target engine torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
    • F02M26/54—Rotary actuators, e.g. step motors

Definitions

  • the invention relates to the field of motor vehicles.
  • It relates more particularly to an engine control valve provided to manage the circulation of a fluid in a duct connected to the engine of the vehicle.
  • Motor control valves actuated by a rotary motor are known and adapted to move in translation a valve disposed in a conduit and for controlling the passage of fluid in this conduit.
  • These valves comprise an electric motor associated with a gear train for rotating a cam system. The displacement in translation generated allows the drive of the valve in a rectilinear motion.
  • EP 1 375 892 describes such a device.
  • the purpose of the invention is to improve this type of valve by proposing a motor control valve whose control is easier and more robust.
  • the invention provides an engine control valve comprising a rotary actuator, a valve, and a device for transforming movement adapted to transform the rotation of the actuator in translation of the valve, characterized in that the device motion transformation comprises a constant pitch helical link for translational drive of the valve.
  • the translation drive of the valve by the motion transformation device is made according to a substantially linear law, that is to say that the axial force exerted on the valve for its opening undergoes variations, depending on the valve lift and therefore the rotation of the actuator, which can be represented by a substantially straight line.
  • This does not allow to obtain a significant reduction in the force applied to the valve from the beginning of the valve lift phase (where the efforts to overcome are the most important), as commonly practiced in the valves of the art prior art in which force decreases rapidly after the start of emergence (see figure 4 , dashed curve), according to a link whose pitch is not constant, or which has a double slope.
  • the valve according to the invention has for its part a transformation device with linear behavior and therefore with improved controllability.
  • Another aspect of the invention is an assembly of such a valve and control means programmed according to a linear model.
  • the control means may comprise conventional electronic devices such as a motor control unit ("Engine Control Unit” in English).
  • the figure 1 represents an engine control valve 1 which is in this example an exhaust gas recirculation valve commonly referred to as "EGR valve".
  • EGR valve exhaust gas recirculation valve
  • the valve 1 comprises a fluid inlet 2 and a fluid outlet 3 between which is disposed the head 4 of a valve 5.
  • the valve 5 in the closed position makes it possible to stop the flow of the fluid entering through the inlet 2 and out through the outlet 3.
  • the full opening of the valve 5 allows the opposite free flow of the fluid while maintaining the valve 5 in an intermediate position allows the dosage of the fluid.
  • the valve 1 comprises a support 6 on which is mounted an actuator, constituted here by an electric motor 7, a motion transformation device 9, and a transmission wheel 8 which allows the motor 7 to drive the motion transformation device 9, the latter transforming the rotary movement of the transmission wheel 8 in rectilinear motion of the valve 5.
  • the movement transformation device 9 has a generally tubular shape and has at one of its ends a valve seat 10 and at the other end of its ends a cam path 11.
  • the valve may be without a seat valve.
  • the cam path 11 comprises two tracks made in a tubular wall 12 of the motion transformation device 9.
  • a bar 13 fixed on the valve 5 and provided with rollers 14 is adapted to cooperate with the cam path 11 .
  • the motion transformation device 9 cooperates with an input wheel 15 having a toothed portion 16 attached to a portion tubular 17 rotatably mounted on the motion transformation device 9 by means of a bearing 18.
  • Elastic return means 19 are here provided in the form of a helical torsion spring for biasing the input wheel 15 in one of its extreme angular positions corresponding in this example to the closed position of the valve 5.
  • the motor 7 is thus actuated against the return means 19 to open the valve 5.
  • a position sensor 20 furthermore allows the position of the valve 5 to be measured at any time along its axial stroke, and this thanks to a feeler 21 held in contact with the bar 13 by means of a spring (not represented). .
  • the sensor 20 has a linear behavior in that the probe 21
  • a protective cover 22 (see figure 2 ) mounted on the support 6 protects the rotating elements of the valve 1.
  • the motor 7 is powered and driven according to a control integrated in a conventional manner to computing means (not shown).
  • the motor 7 When the motor 7 is rotated, it rotates the transmission wheel 8 (and any gear train possibly provided) which in turn rotates the input wheel 15.
  • the latter also drives in rotation the bar 13 by complementarity of shapes (see figure 1 ) while leaving it free in axial translation. This causes rolling of the rollers 14 on the cam path 11 (which is fixed, the motion-transforming device 9 being fixed to the support 6) and consequently the joint translation of the bar 13 and the valve 5 in the axial direction, causing opening or closing of the valve 5.
  • the cam path 11 is configured so that the force exerted on the valve 5 when it opens is substantially linear.
  • the motion transformation device 9 thus has a behavior approaching a linear system.
  • a linear system is a system model that applies a linear (first degree) operator to an input signal.
  • a linear system typically displays much simpler features and properties than the general nonlinear case.
  • the axial force applied to the valve varies linearly or quasi-linearly along the axial stroke of the valve 5.
  • the curve 23 representative of the axial force applied to the valve 5 as a function of its axial stroke (valve lift) is therefore substantially a straight line.
  • this curve 23 is shown in solid lines while a conventional curve 24 relating to the valves of the prior art is shown in dashed lines.
  • the variation of the axial force applied to the valve 5 is not only constant but very low.
  • the force at the beginning of the valve lift (point 25 of the figure 4 ) may be 420 N while the force at the end of the valve lift (point 26 of the figure 4 ) can be 380 N or a force variation of approximately 10% over the entire stroke of the valve 5.
  • the order of magnitude of the change in force for the valves of the prior art is 1000% (see figure 4 ).
  • the curve 23 is here not only a straight line but is moreover quasi-horizontal.
  • the cam path 11 is, in the present example, consisting of two tracks arranged face to face (diametrically opposed) on the tubular wall 12, each of these tracks being here formed of a through opening in the tubular wall 12.
  • the shape of the light is a helicoid extending on the tubular wall 12. In order to obtain a constant variation valve lift axial force, this helicoid is in the present example provided with a constant helix pitch (see FIG. figure 3 ).
  • the opening behavior of the valve 1 is substantially linear in the sense that a rotation of the motor 7 at a given angle will produce substantially the same variation of force on the valve 5, regardless of the position of the valve 5.
  • This variation being furthermore reduced to a minimum here, the rotation of the motor 7 by a given angle will substantially produce the application of the same force on the valve 5 , whatever the position of the valve 5.
  • substantially linear behavior of the motion transformation device 9 may be supplemented by other elements of the kinematic chain from the motor 7 to the valve 5 and also advantageously having a substantially linear behavior.
  • the embodiment of the present example which is particularly advantageous, groups on this kinematic chain only elements with a substantially linear behavior.
  • This kinematic chain can therefore be modeled according to a linear model with satisfactory results.
  • This linear model is present in the electronic device chosen to drive the valve.
  • the motor 7, first of all, is here a DC motor, which gives it a substantially linear behavior.
  • All gearing transmitting the rotation of the motor 7 to the input wheel 15 is also substantially linear behavior, that is to say that the teeth of the toothed wheels (here, the wheels 8 and 15) are regularly distributed on the useful circumference of said wheels.
  • Friction is also a source of non-linearity.
  • the bearing 18 here makes it possible to reduce these friction to bring the system closer to the linear behavior.
  • the helical torsion spring constituting the return means 19 is also here with a substantially linear behavior, that is to say that the rotation of the input wheel 15 is directly proportional to the torque that caused this rotation (the applied torque by the transmission wheel). This behavior is obtained by choosing a substantially constant stiffness spring.
  • the entire kinematic chain from the motor 7 to the valve 5 thus has a substantially linear behavior which improves its controllability.
  • the task of the calculation means (not shown) for the control of the motor 7 is here reduced because, to pass from a position setpoint for the valve 5 to the corresponding command of the motor 7, the calculation means have to manipulate equations linear, requiring less computing power, better responsiveness and greater robustness.
  • the command the motor 7 is here linear, that is to say made according to a linear model, the first degree.
  • the gear train from the motor 7 to the input wheel 15 may comprise any number of wheels or gears.
  • the valve may be any member that provides flow control (opening, closing and / or dosing) by a translational member.
EP10726947.4A 2009-06-17 2010-06-17 Vanne comportant un dispositif de transformation de mouvement Active EP2443332B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0902949 2009-06-17
PCT/EP2010/058549 WO2010146121A1 (fr) 2009-06-17 2010-06-17 Vanne comportant un dispositif de transformation de mouvement

Publications (2)

Publication Number Publication Date
EP2443332A1 EP2443332A1 (fr) 2012-04-25
EP2443332B1 true EP2443332B1 (fr) 2016-11-16

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EP10726947.4A Active EP2443332B1 (fr) 2009-06-17 2010-06-17 Vanne comportant un dispositif de transformation de mouvement

Country Status (6)

Country Link
US (1) US9745901B2 (zh)
EP (1) EP2443332B1 (zh)
JP (1) JP2012530209A (zh)
KR (1) KR20120050967A (zh)
CN (1) CN102482998B (zh)
WO (1) WO2010146121A1 (zh)

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Also Published As

Publication number Publication date
KR20120050967A (ko) 2012-05-21
JP2012530209A (ja) 2012-11-29
US20120138029A1 (en) 2012-06-07
WO2010146121A1 (fr) 2010-12-23
EP2443332A1 (fr) 2012-04-25
CN102482998A (zh) 2012-05-30
US9745901B2 (en) 2017-08-29
CN102482998B (zh) 2017-03-22

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