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WO2002023032A1 - Verin de commande electromoteur a deux etapes, destine a une soupape - Google Patents

Verin de commande electromoteur a deux etapes, destine a une soupape Download PDF

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Publication number
WO2002023032A1
WO2002023032A1 PCT/EP2001/010217 EP0110217W WO0223032A1 WO 2002023032 A1 WO2002023032 A1 WO 2002023032A1 EP 0110217 W EP0110217 W EP 0110217W WO 0223032 A1 WO0223032 A1 WO 0223032A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuator
screw drive
valve
valve according
spindle nut
Prior art date
Application number
PCT/EP2001/010217
Other languages
German (de)
English (en)
Inventor
Bjoern Hagemann
Carsten Horn
Original Assignee
Berger Lahr Gmbh & Co. Kg
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.)
Filing date
Publication date
Application filed by Berger Lahr Gmbh & Co. Kg filed Critical Berger Lahr Gmbh & Co. Kg
Priority to EP01960724A priority Critical patent/EP1320676A1/fr
Publication of WO2002023032A1 publication Critical patent/WO2002023032A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • 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
    • F02M26/50—Arrangements or methods for preventing or reducing deposits, corrosion or wear caused by impurities
    • 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
    • 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
    • F02M26/65—Constructional details of EGR valves
    • F02M26/66—Lift valves, e.g. poppet valves
    • F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • 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
    • F02M26/45—Sensors specially adapted for EGR systems
    • F02M26/48—EGR valve position sensors

Definitions

  • the invention relates to a valve with an actuating device for opening and closing, in particular an exhaust gas recirculation valve for internal combustion engines, the actuating device being connected to an actuator of the valve.
  • Exhaust gas recirculation valves for internal combustion engines are used to reduce the fuel consumption and emissions of diesel and gasoline engines. With the help of this valve, exhaust gases are added to the combustion air, so that a defined amount of oxygen is supplied to the combustion process.
  • pneumatic actuators are used to actuate exhaust gas recirculation valves, but they only allow open / close positions of the valve, which means that no intermediate positions can be positioned.
  • Actuators with a linear gear are already known (US 6089536). This must be for the maximum Adjustment force must be dimensioned over the entire adjustment path, so that this system has a low adjustment speed for a given driving force.
  • An exhaust gas recirculation valve is known from DE 1 98 311 40 A1, which works with a lifting magnet.
  • the fact that the maximum adjusting force is required at the point at which the lifting magnet develops the least force is disadvantageous here.
  • lifting magnets with adjustment paths in the range of several millimeters have the disadvantage of a very high power requirement.
  • the object of the present invention is to provide a valve with an actuating device which, on the one hand, is able to actuate the valve quickly and also with a high counterforce and which also has a comparatively large one
  • the actuating device has an electric motor-driven screw drive connected to the actuator for positioning the actuator over a long distance with a low adjustment force and a stroke actuator connected to the actuator with a short adjustment path and a large adjustment force.
  • the actuators used can be dimensioned according to the different requirements in terms of work requirements, which on the one hand achieves a compact design and on the other hand low power consumption.
  • the appropriate actuator can be activated. High opening forces can be overcome by the stroke actuator with a large adjustment force and a small path, while when the valve is open, the screw drive enables an adjustment and positioning movement over a long stroke distance with a low force and exact positionability.
  • the stroke actuator with a short adjustment path and a large adjustment force is formed by an electric stroke magnet or a piezotranslator.
  • These stroke actuators work with a very small stroke, but this is sufficient for "detaching" for the first part of the opening path, in which a high opening force is required due to the valve sticking together and due to the gas pressure conditions.
  • a stroke of a fraction of a millimeter, for example 100 micrometers, is sufficient to overcome the holding forces acting when the valve is closed. With this small stroke, very high adjustment forces can be applied despite the compact design.
  • a brushless DC motor or a stepper motor is expediently provided as the drive motor for the screw drive having a spindle.
  • drive motors of small size are sufficient, since they only have to be dimensioned in accordance with the comparatively small adjustment forces to be applied when the valve is open. This enables a compact design and high dynamics to be achieved.
  • the actuator formed by a valve stem is rod-shaped and is rotatably connected to a rotor of the electromotive drive and to a spindle, that the stator of the electromotive drive and the stator of the stroke actuator are connected to each other and that to the spindle meshing spindle nut is connected to the core of the stroke actuator.
  • the actuator is rod-shaped with a spindle which meshes with a spindle nut connected to a rotor of the electromotive drive, that the spindle nut is preferably rotationally decoupled from the core of the stroke actuator, and that the stator of the stroke actuator, the stator of the electromotive drive and a linear guide with anti-rotation for the rod-shaped actuator are connected.
  • Both embodiments have in common that they are compact and can therefore be used without problems even in confined spaces. Despite the compact design, both high adjustment forces and long adjustment distances with exact positioning are possible.
  • a format adjustment is also possible with the actuating device according to the invention, in that the lifting spindle actuator is actuated cyclically to achieve high forces over a large adjustment path. The adjustment is made gradually.
  • the solenoid or similar short stroke actuator is actuated, the load moves and when the short stroke actuator is reset, the spindle is adjusted.
  • an embodiment of the invention provides that the stroke actuator is formed by a second screw drive which, in comparison to the first screw drive for positioning the actuator over a long distance with a small adjustment force, has a short adjustment path with a large adjustment force and that the thread pitch of the second Screw drive in particular is significantly smaller than that of the first screw drive.
  • rotary, in particular electromotive drives can be used for the two screw drives. It is preferably provided that the stroke actuator formed by the second screw drive is a rotary magnet
  • a further embodiment of the actuating device provides that the rod-shaped actuator formed by a valve stem is guided in a linear guide with anti-rotation device and is designed in sections as a spindle which meshes with a spindle nut connected to a rotor of the electromotive screw drive that preferably a lifting actuator having a rotating magnet has a threaded piece connected to its rotor with an internal thread with a small pitch, which meshes with a mating threaded piece with an external thread, which mating threaded piece is arranged in a rotationally fixed manner and is rotationally decoupled from the spindle nut or the rotor connected to it.
  • This exemplary embodiment includes an actuating device with two electromotive screw drives.
  • an actuating device provides that the rod-shaped actuator formed by a valve stem in a linear guide
  • Anti-rotation guide and sections is designed as a spindle that meshes with a spindle nut, that the spindle nut is connected via a limit force coupling to the rotor of the electromotive screw drive, which is rotatably connected to a preferably tubular internal thread part, which meshes with the spindle nut carrying an external thread and that this thread has a smaller pitch than the thread between the spindle and the spindle nut.
  • This actuator with two different drive Transmission paths to the actuator only require a single motor drive, the decoupling of the two drive branches being provided by the limit force coupling. For a low adjustment force, the screw drive with the larger thread pitch is activated and after the occurrence of a higher load and exceeding a limit transmission force specified by the limit force coupling, the second screw drive with the smaller thread pitch is activated.
  • only a single motor drive also requires an actuating device in which the stroke actuator with a short adjustment path and a large adjustment force is formed by a planetary gear.
  • the rod-shaped actuator which is preferably formed by a valve stem, is guided in a linear guide with anti-rotation device and is designed in sections as a spindle which meshes with a spindle nut, the spindle and the spindle nut forming the screw drive and the planetary gear between the spindle nut and the rotor of the latter Screw drive is arranged. If the rotor is driven, this rotational movement is transmitted to the spindle nut via the planetary gear.
  • the spindle nut rotates according to the reduction at low speed and, if necessary, high torque. After a certain angle of rotation, the planetary gear is blocked, so that the mechanical reduction stage formed by the planetary gear is inoperative. The spindle nut is thus directly coupled to the speed of the rotor and accordingly runs at a higher speed and a lower level of force.
  • the actuating device comprising the screw drive and the stroke actuator expediently has a sensor which is connected to a measuring and control device which has a switching logic for selectively actuating the screw drive or of the stroke actuator depending on the required actuation force.
  • a measuring and control device which has a switching logic for selectively actuating the screw drive or of the stroke actuator depending on the required actuation force.
  • an angle of rotation sensor system is assigned to the electric motor drive for the screw drive. With the help of the rotation angle sensor, the zero point can be readjusted during operation and thus tolerances and thermal expansion can be compensated.
  • the measuring and control device can detect a blocking of the spindle drive when the adjustment forces are too great for it and then use the lifting magnet or similar lifting actuator to open the valve.
  • a return element preferably a return spring, is expediently provided for returning the actuator to a predeterminable position, in particular in the closed position of the valve.
  • this return spring ensures that the system is reset to a fail-save position, in the present case in particular to the valve's closed position.
  • FIG. 1 shows a longitudinal sectional view of a first exemplary embodiment of an exhaust gas recirculation valve with a
  • 2 is a longitudinal sectional view of a second embodiment of an exhaust gas recirculation valve
  • 3 shows a longitudinal sectional view of a third exemplary embodiment of an exhaust gas recirculation valve with a rotary magnet as the second stroke actuator
  • Fig. 4 is a longitudinal sectional view of a fourth embodiment of an exhaust gas recirculation valve with a single drive and
  • FIG. 5 shows a longitudinal sectional illustration of a fifth exemplary embodiment of an exhaust gas recirculation valve, likewise with a single drive.
  • An exhaust gas recirculation valve 1,1a to 1d shown in FIGS. 1 to 5 is used in an internal combustion engine to recirculate exhaust gas from the exhaust area back into the intake area for the fuel-air mixture.
  • the exhaust gas recirculation valve 1, 1a to 1d is attached to a housing 2 with a return duct 3, the direction of flow of the recirculated combustion gases being identified by the arrows PF1.
  • the return duct 3 can be closed with the aid of a valve 4 designed as a cone valve in the exemplary embodiments, the closing part 5 lying tightly against a valve seat 6 on the housing side in the closed state.
  • An actuating device 7 is provided for opening and closing the valve 4.
  • the rod-shaped valve stem 8 serves as an actuator and connecting element between the closing part 5 of the valve and the actuating device 7.
  • the actuating device 7 has an electric motor-driven screw drive 9 and an electric stroke actuator 10.
  • the in the embodiments of FIG. 1 u. 2 designed as a solenoid 11 stroke actuator has a very short working stroke, but can transmit high forces.
  • the screw drive which in the exemplary embodiment is a spindle drive is designed to adjust the valve over a larger distance and also for precise positioning.
  • Both the stroke actuator 10 and the screw drive 9 are connected to a measuring and control device, not shown here, via which the power supply and control takes place. This measuring and control device also has a switchover logic for selectively actuating either the screw drive or the stroke actuator.
  • the screw drive can have a brushless DC motor or a stepper motor as preferred drive motors.
  • the rotor 12 of the screw drive motor 13 is connected in a rotationally fixed manner to the valve shaft 8 which also forms the rotor shaft.
  • the stator 14 of the motor 13 is arranged around the rotor 12.
  • At the upper end of the valve stem 8 it is provided with a spindle 15 which meshes with a spindle nut 16. If the motor 13 is driven so that its rotor 12 rotates, the spindle 15 moves within the spindle nut 16 in the axial direction, so that the valve can be closed or opened depending on the direction of rotation.
  • the lifting actuator 10 formed in the exemplary embodiment according to FIGS. 1 and 2 by an electrical lifting magnet 11 has a stator 17 and an armature or core 18 which can be moved relative thereto.
  • the stator 17 carries a coil 19 and formed an electromagnet that attracts the core 18 when energized.
  • the core 18 is connected to the spindle nut 16, so that when the lifting magnet 11 is actuated, its lifting movement is transmitted via the spindle nut 16 and the spindle 15 and thus to the valve stem 8. With such a stroke movement, the valve 4 is moved in the opening direction according to the arrow PF2.
  • the stator 17 and the stator 14 of the screw drive 9 form a stationary unit which is connected to a carrier and housing part 21 of the actuating device 7, which is also connected to the housing 2 having the return channel 3.
  • the stroke actuator 10 is designed for a very small stroke movement, which can be, for example, in the tenths of a millimeter range. Such a short working stroke is sufficient, however, to lift a closing part 5, which is stuck in the closed position due to combustion residues and the like, from its valve seat 6. As soon as this has taken place, the valve can be positioned comparatively smoothly, so that the screw drive 9 can then be switched over. An exact intermediate positioning of the closing part 5 and thus an exact adjustment of the passage cross section is then also possible. The valve can thus not only be positioned exactly between a closed position and an open position but also in any intermediate position.
  • the stroke actuator 10 designed for a very short working stroke enables a very compact design and the screw drive 9 can be made very compact in the same way, since it only has to transmit comparatively small adjustment forces.
  • the power supply of the electromechanical lifting magnet 11 can be supported at least by a capacitor discharge or can be formed exclusively by a capacitor discharge. Since the actuation of the solenoid 11 takes place only over a short period of time, the stored capacitor charge is sufficient for actuation in most cases.
  • the power supply device of the lifting magnet can be dimensioned correspondingly small his .
  • a drive-less DC motor is provided as the drive motor 13 for the screw drive 9 in the exemplary embodiment according to FIGS. 1 and 2, which is equipped with a rotation angle sensor system 22 and enables exact positioning.
  • the rotor 12, 12a of the screw drive motor 13 executes a rotary movement over a few revolutions depending on the design of the spindle transmission.
  • a so-called can motor with ring coils which can be mass-produced inexpensively, can be used. Motors of this type are also used for small synchronous motors or for stepper motors.
  • the screw drive motor of the screw drive shown in FIG. 2 is also equipped with such a motor, a rotor 12a having a somewhat modified design being used here.
  • the rotor 12 (FIG. 1) connected to the rotatable valve stem 8 is designed to be somewhat longer than the stator because of the axial stroke adjustment in order to achieve an overlap of the stator and rotor in every position position.
  • a return spring 23 is arranged between the rotor 12 and the core 18 of the lifting magnet 11, which core is fixed in the direction of rotation. Starting from the closed position of the valve so these, embodied as a rotational return spring spring 23 is biased so that is in the 'fault case, the spring-stored energy for closing the valve available. The return spring 23 thus forms a fail-save spring.
  • the exhaust gas recirculation valve 1a according to FIG. 2 is basically constructed in the same way as the exhaust gas recirculation valve 1 according to FIG. 1 and accordingly also has a screw drive 9 and a short stroke actuator 10 in the form of a lifting magnet 11. The main difference is that the mechanical construction according to FIG.
  • valve stem 8 is guided axially in an anti-rotation device 24, which is arranged when the valve stem 8 passes through an opening in the carrier and housing part 21.
  • the section of the valve stem 8 passing through the drive area is designed as a spindle 15a and meshes with a spindle nut 16a which is connected in a rotationally fixed manner to the rotor 12a of the screw drive motor 13.
  • the spindle nut 16a is supported by a roller bearing 25 on the core 18 of the solenoid 11.
  • the valve stem 8 can be moved back and forth when the spindle nut 16a rotates in accordance with the double arrow Pf3 and when the solenoid 11 is actuated, the stroke movement of the core 18 is transmitted via the roller bearing 25 to the spindle nut 16a, which in turn transmits this stroke movement to the spindle 15a or transmits the valve stem 8.
  • the valve stem 8 and the closing part 5 connected to it perform a lifting movement according to the arrow Pf2 in the opening direction of the valve.
  • the fail-save return spring 23 is arranged between the non-rotatable valve stem 8 or a closing part 26 located at its spindle end and the spindle nut 16a rotating during a stroke adjustment by the screw drive 9.
  • 3 and 4 show exhaust gas recirculation valves 1b, 1c which have actuating devices 7 with two screw drives.
  • the first screw drive 9a or 9b is designed for positioning the actuator 8 over a long distance with a low adjustment force
  • the second screw drive 27 (FIG. 3) or 28 (FIG. 4) forming the stroke actuator 10 is designed for a short adjustment path with a large adjustment force This is achieved in that the thread pitch of the second screw drive 27 or 28 is significantly smaller than that of the first screw drive 9a or 9b.
  • valve 3 shows an exhaust gas recirculation valve 1b, in which the actuating device 7 has two screw drives with different thread pitches.
  • the valve stem 8 is formed at its inner end as a spindle 15b which meshes with a spindle nut 16b connected to the rotor 12b of the first screw drive 9a.
  • the second screw drive 27 has a rotary magnet 29 as the drive, the rotor 30 of which is connected to a threaded piece 31, which carries an internal thread 32 with a small pitch.
  • the threaded piece 31 meshes with its internal thread 32 with a counter-threaded piece 33 with an external thread that is arranged in a rotationally fixed and coaxial manner.
  • the counter-thread piece 33 is rotationally decoupled from the spindle nut 16b or the rotor 12b connected to it.
  • a roller bearing 34 is arranged between the rotor 12b and the counter-thread piece 33, via which a pressure transmission is possible.
  • this can engage with a radially inwardly projecting nose in an outer longitudinal groove of the spindle 15b.
  • the first screw drive 9a can be activated, so that the rotor 12b drives the spindle nut 16b and thereby moves the valve stem either in the opening or closing direction. If the rotary magnet 29 is not activated, it is brought back to its original starting position by a return spring 35. As in the other exemplary embodiments, a fail-save return spring 23 is also provided here, by means of which the valve can be brought into the closed position in the event of faults.
  • FIG. 4 shows an embodiment of an exhaust gas recirculation valve 1c, in which the actuating device 7, like the exemplary embodiment according to FIG. 3, has two screw drives with threads of different pitch.
  • the spindle nut 16c is connected to the rotor 12c of the electromotive screw drive 9c via a limit force coupling 36.
  • the spindle nut 16c is thus taken along via the limit force coupling 36 and the valve stem 8 is thereby moved in the closing or opening direction.
  • the spindle nut 16c has an external thread 37 which meshes with a tubular internal thread part 38 which is connected to the rotor 12c in a rotationally fixed manner.
  • the limit force of the limit force coupling arranged between the rotor 12c and the spindle nut 16c 36 exceeded, a relative rotational movement occurs between the internal thread part 38 connected to the rotor 12c and the spindle nut 16c.
  • the thread 37 engaged therebetween has a smaller pitch than the thread between the spindle 15c and the spindle nut 16c, so that in this operating situation a greater driving force acts on the valve stem 8 with a small adjustment path.
  • the limit force coupling 36 is formed by a rotationally prestressed spring which engages at one end on the spindle nut 16c and at the other end on the rotor 12c or the internal thread part 38 connected to it.
  • a stop 39 serves to limit the relative rotation between the spindle nut 16c and the rotor 12c which is caused by the prestressed spring. If the pressure force present by the prestressed spring at the stop 39 is overcome, then a relative rotational movement occurs between the internal thread part 38 and the spindle nut 16c, so that the thread 37 located therebetween provides for a lifting movement of the valve stem 8. This operating case occurs when a certain overload is present, which can occur in particular when the valve is opened for the first time.
  • FIG. 5 shows an exhaust gas recirculation valve 1d with an actuating device 7, which has a screw drive 9d and a stroke actuator 10 formed by a planetary gear 41 with a short adjustment path and a large adjustment force.
  • the valve stem 8 is guided so as to be longitudinally displaceable in a linear guide with anti-rotation device 24 and is designed in sections as a spindle 15d which meshes with a spindle nut 16d.
  • the motor 13b has a rotor 12d which is connected in a rotationally fixed manner to a ring gear 42 which is partially internally toothed.
  • the planetary gear 41 is arranged between the rotor 12d and the spindle nut 16d.
  • the ring gear 42 meshes with a planet gear 43 which is connected to the spindle nut 16d and which meshes with a fixed sun gear 44 arranged coaxially to the spindle nut 16d.
  • a limited rotation allowable rotation stop 45 is provided between the rotor 12d and the spindle nut 16d.
  • the planetary stage is activated when the direction of rotation is reversed, so that a high level of force is available to open valve 4.
  • the spindle nut 16d can be connected to the rotor 12d via a limit force coupling formed by a torsion spring.
  • This torsion spring results in a mechanical preload, by means of which the planetary stage is only used in one direction of rotation from a certain force level. Without such a spring preload, the combination of planetary gear and spindle drive can also be used to increase resolution and dynamics. In this case, the target position can be quickly pre-positioned with a coarse resolution and finely positioned by reversing the direction of rotation using the planetary gear stage.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Mechanically-Actuated Valves (AREA)

Abstract

La présente invention concerne une soupape de recyclage des gaz d'échappement (1) destinée à des moteurs thermiques, présentant un dispositif d'actionnement (7) comprenant un organe de commande formé par une tige de soupape (8). A l'organe de commande (8) est relié un mécanisme d'entraînement à vis électromoteur (9) permettant le positionnement de l'organe de commande sur une course de longueur importante, pour une force de réglage limitée, ainsi qu'un élément électrique d'actionnement de levée (10), relié à l'organe de commande, avec une course de réglage limitée et une force de réglage élevée. Ces éléments d'actionnement (9, 10) peuvent être dimensionnés en fonction des diverses exigences de fonctionnement. Selon la force requise au cours de la course de réglage de la soupape, l'élément d'actionnement (10) peut être utilisé pour des forces d'ouvertures élevées, avec une force de réglage élevée et une course limitée, et le mécanisme d'entraînement à vis (9) peut être utilisé pour un mouvement de réglage et de positionnement exact sur une course importante.
PCT/EP2001/010217 2000-09-12 2001-09-05 Verin de commande electromoteur a deux etapes, destine a une soupape WO2002023032A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP01960724A EP1320676A1 (fr) 2000-09-12 2001-09-05 Verin de commande electromoteur a deux etapes, destine a une soupape

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10044898A DE10044898A1 (de) 2000-09-12 2000-09-12 Ventil
DE10044898.4 2000-09-12

Publications (1)

Publication Number Publication Date
WO2002023032A1 true WO2002023032A1 (fr) 2002-03-21

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EP (1) EP1320676A1 (fr)
DE (1) DE10044898A1 (fr)
WO (1) WO2002023032A1 (fr)

Cited By (9)

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EP1526271A1 (fr) * 2003-10-24 2005-04-27 Cooper-Standard Automotive (Deutschland) GmbH Soupape de recirculation de gaz d'échappement
WO2006071124A1 (fr) * 2004-12-30 2006-07-06 Fmc Kongsberg Subsea As Actionneur antipompage
WO2006095088A1 (fr) * 2005-03-09 2006-09-14 Valeo Systemes De Controle Moteur Dispositif de recirculation de gaz d'echappement comportant une vanne ayant un element de regulation decollable de son siege
EP1724460A1 (fr) * 2005-05-19 2006-11-22 Fujikoki Corporation Vanne actionnée par moteur
CN103133190A (zh) * 2013-03-15 2013-06-05 第一拖拉机股份有限公司 出气口位置双向可调的电动egr阀
EP2778485A1 (fr) * 2013-03-13 2014-09-17 Kohler Mira Limited Vanne
US9182047B2 (en) 2013-03-13 2015-11-10 Kohler Mira Limited Valve with fail-safe device
DE102015119305A1 (de) * 2015-11-10 2017-05-11 Bürkert Werke GmbH Ventillinearantrieb sowie Ventil
DE102018103619B3 (de) 2018-02-19 2019-01-24 Pierburg Gmbh Linearaktuator für ein Ventil eines Kraftfahrzeugs

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DE102005038067B4 (de) * 2005-08-10 2008-12-11 Danfoss A/S Ventilaufsatz für ein Ventil, insbesondere Heizungs- oder Kälteventil
DE102015108155B4 (de) * 2015-05-22 2019-11-21 Bayerische Motoren Werke Aktiengesellschaft Gasregelventil eines Verbrennungsmotors
EP4343183A1 (fr) 2022-09-20 2024-03-27 Johnson Electric Germany GmbH & Co. KG Système d'étanchéité pour soupapes d'écoulement de fluide commutables

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US4561408A (en) 1984-01-23 1985-12-31 Borg-Warner Corporation Motorized flow control valve
DE3618479A1 (de) * 1985-02-28 1987-12-03 Siemens Ag Armatur zum absperren einer stroemung
US4840350A (en) 1987-07-31 1989-06-20 Bendix Electronics Limited Electrically actuated EGR valve
US5318064A (en) * 1993-09-24 1994-06-07 Marotta Scientific Controls, Inc. Motor-operated valve
DE4423313A1 (de) * 1994-07-02 1996-01-04 Pierburg Gmbh Elektromotorisches Stellglied
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US5937835A (en) 1997-06-24 1999-08-17 Eaton Corporation EGR system and improved actuator therefor
DE19753369A1 (de) * 1997-12-02 1999-06-17 Gazzaz Hesham Hassan Steuerschaltung für ein Gaswarnsystem
EP0930428A2 (fr) * 1998-01-16 1999-07-21 Pierburg Aktiengesellschaft Soupape de recirculation de gaz d'échappement
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Cited By (18)

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EP1526271A1 (fr) * 2003-10-24 2005-04-27 Cooper-Standard Automotive (Deutschland) GmbH Soupape de recirculation de gaz d'échappement
RU2402712C2 (ru) * 2004-12-30 2010-10-27 Фмс Конгсберг Сабси Ас Привод клапана и клапанное устройство
WO2006071124A1 (fr) * 2004-12-30 2006-07-06 Fmc Kongsberg Subsea As Actionneur antipompage
GB2437026A (en) * 2004-12-30 2007-10-10 Fmc Kongsberg Subsea As Anti-surge valve
AU2005322697B2 (en) * 2004-12-30 2011-09-01 Fmc Kongsberg Subsea As Anti-surge actuator
GB2437026B (en) * 2004-12-30 2009-09-02 Fmc Kongsberg Subsea As Anti-surge actuator
WO2006095088A1 (fr) * 2005-03-09 2006-09-14 Valeo Systemes De Controle Moteur Dispositif de recirculation de gaz d'echappement comportant une vanne ayant un element de regulation decollable de son siege
FR2883038A1 (fr) * 2005-03-09 2006-09-15 Valeo Sys Controle Moteur Sas Dispositif de recirulation de gaz d'echappement comportant une vanne ayant un element de regulation decollable de son siege
EP1724460A1 (fr) * 2005-05-19 2006-11-22 Fujikoki Corporation Vanne actionnée par moteur
US7494108B2 (en) 2005-05-19 2009-02-24 Fujikoki Corporation Motor-operated valve
EP2778485A1 (fr) * 2013-03-13 2014-09-17 Kohler Mira Limited Vanne
US9182047B2 (en) 2013-03-13 2015-11-10 Kohler Mira Limited Valve with fail-safe device
US9644757B2 (en) 2013-03-13 2017-05-09 Kohler Mira Limited Valve with fail-safe device
US10443751B2 (en) 2013-03-13 2019-10-15 Kohler Mira Limited Valve with fail-safe device
CN103133190A (zh) * 2013-03-15 2013-06-05 第一拖拉机股份有限公司 出气口位置双向可调的电动egr阀
DE102015119305A1 (de) * 2015-11-10 2017-05-11 Bürkert Werke GmbH Ventillinearantrieb sowie Ventil
DE102018103619B3 (de) 2018-02-19 2019-01-24 Pierburg Gmbh Linearaktuator für ein Ventil eines Kraftfahrzeugs
WO2019158331A1 (fr) 2018-02-19 2019-08-22 Pierburg Gmbh Actionneur linéaire pour une soupape de véhicule à moteur

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