WO2011141533A1 - Actionneur pour un organe de fermeture d'un canal sous pression - Google Patents

Actionneur pour un organe de fermeture d'un canal sous pression Download PDF

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Publication number
WO2011141533A1
WO2011141533A1 PCT/EP2011/057662 EP2011057662W WO2011141533A1 WO 2011141533 A1 WO2011141533 A1 WO 2011141533A1 EP 2011057662 W EP2011057662 W EP 2011057662W WO 2011141533 A1 WO2011141533 A1 WO 2011141533A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuator
spring force
closure member
storage means
force storage
Prior art date
Application number
PCT/EP2011/057662
Other languages
German (de)
English (en)
Inventor
Wilfried Von Der Ahe
Manfred Bartscht
Bodo Bücker
Volker Stebner
Keramettin Seven
Eckart Wirries
Hagen MÜLLER
Norbert BRÄUTIGAM
Original Assignee
Hella Kgaa Hueck & Co.
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 Hella Kgaa Hueck & Co. filed Critical Hella Kgaa Hueck & Co.
Publication of WO2011141533A1 publication Critical patent/WO2011141533A1/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
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • F16K31/045—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means with torque limiters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F02B37/186—Arrangements of actuators or linkage for bypass valves

Definitions

  • the present invention relates to an actuator for a closure member of a gaseous medium-carrying pressure channel, in particular for a closure member of a bypass duct of an exhaust gas turbocharger of an internal combustion engine, comprising an electromotive actuator, a coupling means, by means of which the electromotive actuator is coupled to the closure member, and a Spring force storage means, wherein by means of the electromotive actuator and the spring force storage means, a force can be generated, which can act on the adjusting means against the flow pressure of the gaseous medium via the coupling means.
  • Actuators of the type mentioned are known from the prior art in different embodiments. They may be provided in particular for a closure member of a bypass duct of an exhaust gas turbocharger of an internal combustion engine. Exhaust gas turbochargers for increasing the performance of internal combustion engines have long been known from the prior art. To regulate the charge pressure is in the known exhaust gas turbochargers a closure member, which may be designed in particular as a flap, provided in the exhaust stream. The closure member, which is often referred to as a waste gate valve, is capable of regulating the flow of exhaust gas past the turbine of the exhaust gas turbocharger, or at least partially through the bypass past the turbine.
  • the closure member is opened by an actuator on the compressor side and then directs at least a portion of the exhaust gases past the turbine directly into an exhaust system, so that a further increase in turbine speed can be prevented.
  • the passage through the bypass duct when the closing member is open thus allows excess amounts of exhaust gas, which are not required to drive the turbine of the exhaust gas turbocharger, to be diverted into the exhaust system unused.
  • a pivotable closure flap can be used as closure element. In the closed position, in which the closing flap completely closes the bypass channel, the connection end flap of the actuator, which is coupled via an actuating element with the closure flap, frictionally pressed against a stop which is designed so that it can seal the bypass channel together with the closure flap.
  • pneumatic actuators are generally used in the prior art.
  • the charge pressure built up on the compressor side serves as a pneumatic auxiliary energy for opening the closure member with the aid of the pneumatic actuator.
  • These pneumatic actuators as actuators for the closure member are internally often equipped with a spring element which can support the actuating force of the actuator in one or the other adjustment direction.
  • a pulse-width-modulated clock valve is provided, which can scale the overpressure applied to the actuator to a specific dimension necessary for the respective position.
  • the entire system is intrinsically safe. This means that the actuator opens the shutter when the pressure on the compressor side exceeds a certain maximum value.
  • pneumatic actuators are relatively inexpensive, but have problems due to their systemic elasticities in terms of their positioning speed and their positioning accuracy.
  • DE 10 2008 014 609 A1 discloses an actuator for a switching element of an internal combustion engine, in which an electromotive actuator acts on the switching element via a transmission.
  • the transmission has an elastic element, which can limit the maximum forces or moments on the switching element in at least one direction of adjustment.
  • DE 10 2007 039 218 A1 discloses an actuator for a wastegate of a turbine of an exhaust gas turbocharger of an internal combustion engine with two pressure chambers and a separating element, which separates the two pressure chambers from each other and a pressure acting on the separating element in the second pressure chamber. arranged spring.
  • An actuator connects the separator to the waste gate, thus transferring movement of the separator to the waste gate.
  • the spring acts on the separating element in the closing direction of the waste gate with a force.
  • turbo's own boost pressure is always used to control the actuator, systematically limits the operation of the closure member to those operating areas in which the necessary charge pressure is available at all. This means that the bypass valve can not be opened in any operating condition, so that it is not possible to achieve the greatest possible fuel efficiency in any operating condition.
  • the present invention sets and makes it its mission to provide an actuator for a gaseous medium leading pressure channel, in particular for a closure member of a bypass duct of an exhaust gas turbocharger of an internal combustion engine, which has a higher adjustment speed and a higher Verstellgenautechnik and the In addition, high forces over a relatively large adjustment range can deliver at the same time low power consumption.
  • An inventive actuator for a closure member of a gaseous medium-carrying pressure channel is characterized in that the electromotive actuator and the spring force storage means are designed so that via the coupling means on the closure member a non-linear, dependent on the respective position of the closure member force profile can be generated.
  • the actuator according to the invention advantageously allows an actuation of the closure member, which preferably comprises a closure flap, in any operating condition, regardless of the pressure acting on the closure member.
  • the invented Actual actuator is particularly suitable for a closure member of a bypass duct of an exhaust gas turbocharger of an internal combustion engine. This actuator in particular allows a more fuel-efficient operation of the exhaust gas turbocharger.
  • the spring force storage means may be designed in particular as a compression spring, tension spring, leg spring, leaf spring or the like.
  • the electromotive actuator which may in particular comprise a DC motor
  • the spring force storage means are designed so that the range of the largest restoring forces in a working range of 0 to about 20% of the travel of the closure member can be generated.
  • This relatively large area, in which high actuating forces are provided is due to the large thermal expansion of the closure member, due to a wear-related prediction of the tolerances of about 5% and the pressure drop characteristic of the gas flow.
  • the DC motor of the electromotive actuator must be able to deliver the electrical power dissipated by its own current flow as a heat flow in an environment of 160 ° C.
  • the actuator can advantageously deliver high forces over a comparatively large adjustment range together with a comparatively low current consumption.
  • the electromotive actuator comprises a driven wheel with an eccentric arranged thereon driver which is connected to the coupling means and is coupled via a power transmission means with the spring force storage means.
  • the power transmission means may be configured so that the torque acting on the output gear is variable in dependence on the position of the driver with respect to the power transmission means.
  • the force transmission means comprises a pressure bar, which in particular can be pivotable about a pivot axis.
  • a particularly robust embodiment of the power transmission means can be achieved.
  • the pressure bar is formed integrally with the spring force storage means.
  • the pressure bar may have a contour surface whose contour is adapted to a torque curve corresponding to the force curve as a function of the rotational position of the driven wheel.
  • the driver runs along the contour surface, so that a non-linear torque curve can be obtained in dependence on the respective position of the driver.
  • the actuator should be designed so that the spring support in the actuator can compensate for the externally applied gas forces in each adjustment position of the closure member, so that the electric motor actuator requires only very small currents for positioning or holding the adjustment.
  • this approach is very much idealized and simplified, since the external gas forces acting on the closing organ can be subject to certain fluctuations and thus are not always constant.
  • the spring force storage means is adapted to the acting on the adjusting means in the center gas forces. Such an adjustment of the spring force on the average gas forces is advantageous because in this way the motor current can be minimized in both directions. Much of the resulting force is provided by the spring force storage means, whereas a much smaller portion is provided by the electromotive actuator.
  • the actuator is housed in a housing made of a thermally conductive material, in particular in an aluminum housing, to ensure good heat dissipation during operation of the actuator.
  • the actuator advantageously has a correspondingly adapted seat for the DC motor.
  • a varnishleittress between the DC motor and the housing of the actuator is preferably realized by means of a press fit, a non-positive connection and / or a heat transfer medium (for example by a varnishleitpad or a thermal grease).
  • the actuator has a position sensor means, by means of which the rotational position of the driven gear can be detected.
  • FIG. 1 shows a schematically greatly simplified functional representation of an actuator for a closure member of a gaseous medium-carrying pressure channel according to a preferred embodiment of the present invention
  • Fig. 2 is a schematic representation of the actuator constructed in accordance with a preferred embodiment of the present invention.
  • Fig. 3 is a graphical representation of the force and torque curve, which occurs during operation of the actuator on the closure member or on a driven gear of the actuator.
  • the closure member 2 is in this embodiment, a bypass valve (also called waste gate valve) for a bypass duct of an exhaust gas turbocharger of an internal combustion engine.
  • the closure member 2 is arranged on the exhaust side of the exhaust gas turbocharger and is capable of selectively opening and closing the bypass channel for an exhaust gas turbine of the exhaust gas turbocharger.
  • the closure member 2 comprises a closure flap 20 which can be pivoted about a pivot axis 21. In the closed position, the closure flap 20 encloses an angle of 90 ° with a 0 ° reference line shown horizontally in FIG. 1.
  • the closure member 2 is able to regulate the flow of exhaust gas through the turbine of the exhaust gas turbocharger or at least partially through the bypass duct on the turbine over.
  • the closure member 2 is opened by the actuator 1 on the compressor side and then passes at least a portion of the exhaust gases past the turbine directly into an exhaust gas System, so that a further increase in the turbine speed can be prevented.
  • the passage through the bypass duct when the closure member 2 is open thus allows excess amounts of exhaust gas, which are not required to drive the turbine of the exhaust gas turbocharger, to be used unused in the exhaust system.
  • the closure flap 20 of the actuator 1 which has a coupling means 4, by means of which it is mechanically coupled to the closure flap 20, pressed non-positively to a stop.
  • the stop is designed so that it can effectively seal the bypass channel in cooperation with the closure flap 20.
  • the closure flap 20 When the closure member 2 is to be opened, the closure flap 20 is pivoted about the pivot axis 21 in the arrow direction, for example, into the pivot position shown in FIG. In this position, the exhaust gases can flow at least partially through the then released bypass channel, bypassing the turbine of the exhaust gas turbocharger in the exhaust system.
  • the flow direction of the exhaust gases is also symbolized in Fig. 1 by an arrow.
  • the flow of the exhaust gases thus acts on the closure flap 20 with a force such that the closure flap 20 is to be forced into its open position.
  • the closure flap 20 With the aid of the actuator 1, the closure flap 20 can be held on the one hand in its closed position and, on the other hand, can be pivoted into an open position in a controlled manner.
  • the actuator 1 has an electromotive actuator 3, which is mechanically coupled via the coupling means 4 with the closure flap 20 of the closure member 2.
  • the actuator 1 is designed so that it can exert a counter-pressure on the closure flap 20 via the coupling means 4, so that unintentional opening of the closure flap 20 can be effectively prevented.
  • the closure flap 20 can be opened controlled by means of the actuator 1, so that at least part of the exhaust gases can flow into the bypass channel while bypassing the turbine.
  • the electromotive actuator 3 of the actuator 1 comprises, with further reference to FIG. 2, a direct current motor (DC motor) not explicitly shown here, a transmission means 30 and a rotatable driven gear 31, on which a driver 32 is arranged eccentrically.
  • the transmission means 30, which is preferably a three-stage spur gear, transmits the engine power of the DC motor to the output gear 31.
  • the coupling means 4 for actuating the shutter 20 is connected to the driver 32 and may in particular comprise a coupling linkage.
  • the actuator 3 is housed in a housing made of a thermally conductive material, in particular in an aluminum housing, to ensure good heat dissipation during operation of the actuator 3.
  • a housing made of a thermally conductive material in particular in an aluminum housing, to ensure good heat dissipation during operation of the actuator 3.
  • the actuator 3 preferably has a correspondingly adapted seat for the DC motor.
  • a varnishleittress between the DC motor and the housing of the actuator 3 is preferably realized by means of a press fit, a non-positive connection and / or a heat transfer medium (for example by aciteleitpad or a thermal paste).
  • the electromotive actuator 3 of the actuator 1 is supported in this case by a spring force.
  • the actuator 1 comprises for this purpose a spring force storage means 5, which may be embodied in particular in the form of a compression spring, tension spring, leg spring, leaf spring or the like.
  • the spring force of the spring force storage means 5 acts via a force transmission means on the driver 32 of the driven gear 31.
  • the force transmission means is designed as a pressure beam 6 which is rotatable about a rotation axis 60.
  • the force of the spring force storage means 5 is transmitted to the driver 32 of the driven wheel 31, which in turn is coupled via the coupling means 4 with the closure flap 20.
  • the pressure bar 6 is profiled in such a way that it generates a specific torque curve on the driven wheel 31, which will be discussed in more detail below.
  • the torque curve is adapted to the force curve required to actuate the closure flap 20, and is preferably set to compensate for the average gas forces of the exhaust gases acting on the closure flap 20 in the manner described above and attempting to move it to its open position such that the DC motor of the electromotive actuator 3 requires only relatively small currents for moving and holding the closure flap 20. Due to the low power consumption, the heat generation during the operation of the DC motor can be reduced in a very advantageous manner.
  • the actuator 3 comprises a position sensor means, by means of which the rotational position of the driven gear 31 can be detected.
  • the DC motor can be operated in two opposite directions of rotation, so that the driver 32 can be transferred from a start position, designated "start” in FIG. 2, into an end position, designated “stop", and back again.
  • the pressure bar 6, by means of which the force of the spring force storage means 5 is transmitted to the driver 32 of the output gear 31, has a contour surface 61 which is contoured so that the torque curve shown in Fig. 3 can be obtained.
  • the rotation of the driven wheel 31 from the starting position of the driver 32 in its end position takes place in the direction of the arrow (thus, according to this diagrammatic perspective, in a clockwise direction).
  • the contour surface 61 of the pressure bar 6 initially has a planar contour. If half of the possible angle of rotation of the output gear 31 is exceeded, the contour of the contour surface is curved. This particular shaping of the contour surface 61 of the pressure beam 6 leads to the specific torque curve, which is shown in FIG.
  • Fig. 3 the force and torque conditions during the opening of the closure flap 20 of the closure member 2 are shown. Shown are the torque MAW as a function of the angular position of the driver 32 on the output gear 31 and the effective means of the coupling means 4 on the closure flap 20 force FWG function of the angular position of the closure flap 20. It is clear that in the closed position and to to an angular position of the closure flap 20 of slightly less than 85 ° (the closed position has already been defined above as the 90 ° position) a substantially constant force (in a sense a force plateau) of slightly more than 300 N on the coupling means 4 acts on the closure flap 20. This is the area of the largest stellar forces.
  • the force acting on the closure flap 20 decreases substantially linearly up to an angular position of about 65 °.
  • the resulting force acting on the closure flap 20 is then slightly less than 50 N. If the displacement angle is further increased, the force remains almost constant. Up to an adjustment angle of 40 °, the force gradually increases to slightly more than 50 N.
  • the torque curve on the output gear 31 is non-linear.
  • a torque of about 2 Nrn When the closure flap 20 is in its closed position (150 ° position of the driver 32), a torque of about 2 Nrn.
  • the electric motor actuator 3 When the flap 20 is pivoted and thus the bypass channel to be opened, the electric motor actuator 3 is activated and the torque of Actuator 1, which acts on the coupling means 4 via the driver 32, rises to a displacement angle of the driven wheel 31 of the actuator 1 of slightly less than 130 ° to its maximum value of slightly more than 3 Nm. Subsequently, the torque drops continuously to slightly more than 0.5 Nm at a displacement angle of the driven gear 31 of 90 °.
  • the driver 32 first moves along the planar course of the contour surface 61.
  • the actuator 1 is mechanically designed so that the spring force storage means 5 can ideally compensate for the acting on the outside of the closure flap 20 gas forces in each adjustment position.
  • the DC motor of the electromotive actuator 3 then requires only minimal currents for positioning and holding the closure flap 20. This approach is naturally highly idealized, since in particular the external gas forces acting on the closure flap 20 can vary. Therefore, the actuator 1 is preferably designed for the mean acting gas forces.
  • the spring force storage means 5 is designed for acting on the average gas forces, so that the motor current required for the operation of the DC motor is minimized in both directions.
  • the non-linear torque curve on the output gear 31, which is caused by the internal spring force of the spring force storage means 5, allows a suitable design of the resulting force over the entire adjustment of the shutter 20.
  • a low-current operation of the DC motor can be made possible only too small Warming leads.
  • the remaining about 30% are caused by the DC motor of the electric motor actuator 3.
  • the motor currents can be kept low in an advantageous manner.
  • the pressure bar 6 is formed integrally with the spring force storage means 5.
  • a leaf spring with a corresponding, acting as a pressure bar 6 profiling or a leg spring with a specially profiled acting as a pressure bar 6 extension on one of the legs can be provided.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un actionneur (1) pour un organe de fermeture (2) d'un canal sous pression guidant un milieu gazeux, en particulier pour un organe de fermeture (2) d'un canal de dérivation d'un turbocompresseur à gaz d'échappement d'un moteur à combustion interne, comprenant un mécanisme de commande électromotorisé (3), un moyen d'accouplement (4) au moyen duquel le mécanisme de commande électromotorisé (3) est accouplé avec l'organe de fermeture (2), et un moyen accumulateur de force de ressort (5), une force qui peut agir par l'intermédiaire du moyen d'accouplement (4) contre la pression d'écoulement du milieu gazeux sur l'organe de fermeture (2) pouvant être générée au moyen d'un mécanisme de commande électromotorisé (3) et du moyen accumulateur de force de ressort (5) et le mécanisme de commande électromotorisé (3) et le moyen accumulateur de force de ressort (5) étant conçus de telle manière qu'une variation non linéaire de la force, dépendant de la position du moment de l'organe de fermeture (2), puisse être générée sur l'organe de fermeture (2) par l'intermédiaire du moyen d'accouplement (4).
PCT/EP2011/057662 2010-05-14 2011-05-12 Actionneur pour un organe de fermeture d'un canal sous pression WO2011141533A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010020617 DE102010020617A1 (de) 2010-05-14 2010-05-14 Aktuator für ein Verschlussorgan eines Druckkanals
DE102010020617.2 2010-05-14

Publications (1)

Publication Number Publication Date
WO2011141533A1 true WO2011141533A1 (fr) 2011-11-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/057662 WO2011141533A1 (fr) 2010-05-14 2011-05-12 Actionneur pour un organe de fermeture d'un canal sous pression

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DE (1) DE102010020617A1 (fr)
WO (1) WO2011141533A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102767427A (zh) * 2012-06-28 2012-11-07 康跃科技股份有限公司 涡轮增压器的分段式行程特性气动执行器装置

Citations (7)

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Publication number Priority date Publication date Assignee Title
US4089173A (en) * 1975-04-24 1978-05-16 Etat Francais Supercharged internal combustion engines
US5701741A (en) * 1993-11-11 1997-12-30 Alliedsignal, Inc. Turbochargers for internal combustion engines
DE10224051A1 (de) * 2002-05-31 2003-12-11 Bosch Gmbh Robert Vorrichtung zum Betätigen von Verstellkomponenten
DE10250397A1 (de) * 2002-10-29 2004-05-19 Siemens Ag Verfahren zur Ermittlung der Ventilstellung eines Ladedruckventils und zugehörige Vorrichtung
DE102004031230A1 (de) * 2004-06-29 2006-01-19 Audi Ag Vorrichtung und Verfahren zur Ladedruckregelung
DE102007039218A1 (de) 2007-08-20 2009-02-26 Volkswagen Ag Aktuator für ein Wastegate
DE102008014609A1 (de) 2008-03-17 2009-09-24 Continental Automotive Gmbh Aktuator für Schaltelement einer Verbrennungskraftmaschine

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
DE102004002114B4 (de) * 2004-01-14 2006-06-01 Ab Elektronik Gmbh Fahrpedaleinheit mit Kraftsprung-Element
DE102004027499B4 (de) * 2004-06-04 2006-02-23 Ab Elektronik Gmbh Pedaleinheit für ein Kraftfahrzeug
DE102008049251B4 (de) * 2008-09-26 2021-01-21 Pierburg Gmbh Stellvorrichtung zur Umwandlung einer rotatorischen Bewegung in eine lineare Bewegung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4089173A (en) * 1975-04-24 1978-05-16 Etat Francais Supercharged internal combustion engines
US5701741A (en) * 1993-11-11 1997-12-30 Alliedsignal, Inc. Turbochargers for internal combustion engines
DE10224051A1 (de) * 2002-05-31 2003-12-11 Bosch Gmbh Robert Vorrichtung zum Betätigen von Verstellkomponenten
DE10250397A1 (de) * 2002-10-29 2004-05-19 Siemens Ag Verfahren zur Ermittlung der Ventilstellung eines Ladedruckventils und zugehörige Vorrichtung
DE102004031230A1 (de) * 2004-06-29 2006-01-19 Audi Ag Vorrichtung und Verfahren zur Ladedruckregelung
DE102007039218A1 (de) 2007-08-20 2009-02-26 Volkswagen Ag Aktuator für ein Wastegate
DE102008014609A1 (de) 2008-03-17 2009-09-24 Continental Automotive Gmbh Aktuator für Schaltelement einer Verbrennungskraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102767427A (zh) * 2012-06-28 2012-11-07 康跃科技股份有限公司 涡轮增压器的分段式行程特性气动执行器装置

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