EP3087575B1 - Electromagnetic actuating mechanism - Google Patents

Electromagnetic actuating mechanism Download PDF

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Publication number
EP3087575B1
EP3087575B1 EP14828454.0A EP14828454A EP3087575B1 EP 3087575 B1 EP3087575 B1 EP 3087575B1 EP 14828454 A EP14828454 A EP 14828454A EP 3087575 B1 EP3087575 B1 EP 3087575B1
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EP
European Patent Office
Prior art keywords
plunger
armature
movement
stroke
unit
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EP14828454.0A
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German (de)
French (fr)
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EP3087575A1 (en
Inventor
Timo Rigling
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ETO Magnetic GmbH
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ETO Magnetic GmbH
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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/121—Guiding or setting position of armatures, e.g. retaining armatures in their end position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/13—Electromagnets; Actuators including electromagnets with armatures characterised by pulling-force characteristics
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1638—Armatures not entering the winding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets

Definitions

  • the present invention relates to an electromagnetic actuator according to the preamble of the main claim. Furthermore, the present invention relates to a camshaft adjusting system comprising such an electromagnetic actuating device in conjunction with a camshaft adjusting device of an internal combustion engine as preferred use of the electromagnetic actuating device.
  • the object of the present invention is therefore, with improved (in particular accelerated and gleichcolotem) control behavior of the plunger means to reduce the requirements of magnetic force and magnet arm of the armature unit, thus potentially the size of a generic electromotive actuator (both in the radial, and potentially in the axial direction) to reduce and thus to provide a device which combines favorable dynamic properties with a comparatively long effective working stroke of the plunger means.
  • the armature unit provided movable relative to the plunger means, so that the armature unit (preferably along its armature stroke) drive and can take along the plunger means, but the plunger means movable relative to the armature unit additionally a plunger stroke caused by the spring means according to the invention, can perform, which is inventively larger than the armature stroke itself.
  • the axially coupled arrangement of armature unit and plunger means cooperates with force application means acting on the shell side on the plunger means in the form of the pressure body according to the invention, which has adjacent ramps both with the ramp or cone section on the plunger means and with the plunger sections of larger or smaller diameter - or cone section cooperate can.
  • this arrangement is designed and dimensioned such that the armature unit entrains the plunger means along the direction of movement during its armature movement, whereby the plunger means are advanced as far as the (at least one, preferably radially predominantly distributed) pressure body until the cone or ramp (related to the / the pressure body) is overcome.
  • the further feed then happens by expansion of the spring means according to the invention (which have already already supported the armature movement to the armature stroke).
  • the combined action of both the anchor means, as well as the spring means, on the plunger means to an effective ram stroke, which is greater than the actual armature stroke; in practical embodiments of the invention, at least a factor of 1.5, more preferably at least a factor of 2.5.
  • the adjusting device according to the invention can be dimensioned to a much smaller armature stroke (with corresponding advantages of the mechanics and the construction volume), relative to an achievable control stroke.
  • the ramp or cone section according to the invention has an equally advantageous effect on the return of the adjusting device or the plunger means to the starting position.
  • the plunger means are reset from the engagement position (for example, by the engagement in the adjustment groove provided in the preferred use form "camshaft adjustment") only so far against the direction of movement, until - axially - the pressure body (s) reaches the ramp. or cone section reaches / s.
  • the shell-side force acting on the ramp or cone section to a further provision or force application of the plunger means in the direction of the starting position lead without this (in addition to the adjusting partner)
  • the anchor unit itself must have an armature stroke smaller than the ram stroke.
  • the pressure body is preferably a ball or spherical portion of a differently shaped pressure body, other variants are conceivable; It is nevertheless advantageous to arrange the pressure body, more preferably pretensioned by the pretensioning force of a compression spring which is preferably oriented radially to the direction of movement, in a plurality and around a circumference of the plunger means, so that a reliable influencing of the plunger movement by these pressure bodies can take place ,
  • a concrete arrangement of the spring is arbitrary and may depend on the circumstances in the surrounding housing; This also applies to the specific design of a spring.
  • the geometry of the ramp or cone section is important; In practical implementation, it has been found preferable to provide an extension of the ramp or cone section, which is greater than a (maximum) axial extent of the pressure hull, that is about a ball diameter.
  • a pitch angle of the Rampen- or cone section (as measured in longitudinal section relative to the longitudinal axis of movement) in the range between 20 ° and 60 °, preferably between 30 ° and 50 ° to provide.
  • the spring means more preferably realized as a pressure and / or coil spring, in a (hollow cylindrical) interior of the radially symmetrical tappet means provided;
  • the plunger means may have approximately a hollow cylindrical interior and / or an inner annular shoulder.
  • the spring means would then be able to support, for example, a portion of a housing guiding the plunger means, so that according to the invention the spring means can make their contribution to accelerating the plunger unit, wherein the armature unit can continue to have permanent magnet means as before and in otherwise known manner, alternatively but also electromagnetically operable in other ways relative to the stationary core unit.
  • the armature unit (or caused in the actuator electromagnetic drive of the armature unit) monostable to design, ie only provide an anchor initial position as a single stable end position, in which case while energizing the coil means though the armature unit is moved around the armature, after completion of the energization, however, the armature unit falls back into the armature's starting position.
  • This configuration is advantageous in cooperation with the plunger means in that the armature unit after the initial driving of the plunger means makes no contribution to further advancement of the plunger means (this is rather taken over by the spring means) while then returning, in particular by the interaction between the pressure body and Rampen- or cone section, no additional return or take along the anchor unit is necessary in the starting position.
  • an apparatus is provided by the present invention which significantly prolongs effective stroke length of existing generic actuators without requiring equally larger or bulkier magnet assemblies. Accordingly, there are significant advantages, in particular for the preferred application context "camshaft adjustment", not least in the manufacturing effort and in the space required installation space.
  • the present invention is not limited to this application context, but rather is also suitable for any other actuating applications in which long staging strokes are to be realized with limited electromagnetic means.
  • the reference numeral 10 symbolically shows an armature unit with an elongated armature tappet 12 and an armature body 14 which is widened relative to it.
  • the armature unit 10 is movable in an otherwise known manner relative to a stationary core unit (not shown), between an anchor home position ( Fig. 1 , right) and an armature feed position ( Fig. 1 , left half).
  • a typical armature stroke is in the range between 1 and 1.5 mm with an effective stroke of the plunger means of about 4 mm.
  • a plunger unit (plunger means) 16, which is guided in a surrounding plunger housing 18.
  • the plunger unit 16 is open on the bottom side for receiving the armature tappet portion 12; this is dimensioned so that it is in the anchor position ( Fig.1 , right half) a - small - distance from the plunger complies and only at feed the plunger 16 then along the direction of movement (in the plane of the figure Fig. 1 down).
  • a coil spring 22 is shown, which is supported at the other end of a ring bottom 24 of the plunger housing 18.
  • the coil spring 22 is correspondingly compressed and exerts a maximum bias on the plunger unit 16 in the downward direction of movement.
  • the ram unit 16 has, in the direction of the armature unit 10, a tappet portion 26 larger outside diameter; via a cone section 28, this (larger) outer diameter tapers in an engagement-side front tappet section 30 of reduced outer diameter.
  • the cone section 28 extends over an axial length of about 1.2 mm at an angle with respect to the vertical axis of motion of about 25 °.
  • the axial extent (axial length) of the cone portion 28 corresponds to the armature stroke, plus the (gap) distance between an engagement end 34 of the plunger unit and the actuator in the disengaged state.
  • grip pressure body 32 in the form of distributed around the circumference of the plunger unit 16 around balls on the lateral surface of the plunger unit; These balls 32 are biased by their own, horizontally (and thus radially to the longitudinal movement axis) extending compression springs 33.
  • Engaging side i. opposes the armature unit 10
  • the plunger unit 16 forms the engagement portion (engagement end) 34, which is dimensioned to cooperate with a shift groove 36 of an exemplary shown as a control partner shift gate 38 of a camshaft adjustment system;
  • the double arrow 40 illustrates the groove depth in the example shown by about 3.7 mm, which is covered by the ram stroke (here about 4 mm).
  • the left area of the Fig. 1 shows the fully ejected state of the armature plunger 16 from the housing 18.
  • the plunger unit 16 has a total stroke of about 4 mm performs and engages in this state in the groove 36 of the adjusting partner 38 a.
  • the camshaft adjustment takes place in an otherwise known manner.
  • the adjusting groove 36 also causes the return of the plunger 16 along a first return stroke section; Concretely, a decreasing groove depth (upon rotation of the gate 38) causes the plunger unit 16 to move in the return direction (ie in the plane of the figure) Fig. 1 pushed upward).
  • the device shown here is dimensioned such that this provision takes place axially as far along the first return stroke until the balls 32 engaging on the cylindrical lateral surface 26 reach the beginning of the cone section 28 (acting as a ramp). To this Time then leads the radial application of force to the balls 32 as a pressure body to that along the conical surface, the return movement is continued in the direction of the starting position, the cone so far a subsequent to the first return stroke of the groove second return stroke, to the in the Fig.
  • the plunger unit 16 in this return operation does not additionally reset the anchor unit 10 with (about by entrainment of the section 12), but took place immediately after the Bestromungsende already when taking out the plunger 16 is a falling back the anchor unit 10 in its monostable end position ( Fig. 1 , right).
  • a bistable design for example by means of a permanently magnetically realized anchor body 14, be useful, especially with regard to a so realized (magnetic field detected) position, motion and / or reset device.

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  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Electromagnets (AREA)

Description

Die vorliegende Erfindung betrifft eine elektromagnetische Stellvorrichtung nach dem Oberbegriff des Hauptanspruchs. Ferner betrifft die vorliegende Erfindung ein Nockenwellen-Verstellsystem aufweisend eine solche elektromagnetische Stellvorrichtung in Verbindung mit einer Nockenwellen-Verstellvorrichtung eines Verbrennungsmotors als bevorzugte Verwendung der elektromagnetischen Stellvorrichtung.The present invention relates to an electromagnetic actuator according to the preamble of the main claim. Furthermore, the present invention relates to a camshaft adjusting system comprising such an electromagnetic actuating device in conjunction with a camshaft adjusting device of an internal combustion engine as preferred use of the electromagnetic actuating device.

Aus dem Stand der Technik sind gattungsgemäße elektromagnetische Stellvorrichtungen allgemein bekannt; so beschreibt etwa die DE 201 14 466 U1 der Anmelderin den strukturellen Aufbau einer solchen, zur Nockenwellenverstellung eingesetzten Stellvorrichtung. Dabei wird bei Bestromung einer stationären Spuleneinheit eine relativ zu dieser sowie zu einer stationären Kerneinheit bewegbare Ankereinheit angetrieben. Eine an der Ankereinheit ansitzende, langgestreckte und endseitig zum Eingreifen in eine Nockenwellen-Verstellnut der Verstellvorrichtung ausgebildete Stößeleinheit wird durch die Ankereinheit in eine Eingriffsstellung gebracht und bewirkt in dieser die gewünschte Nockenwellenverstellung. Die Verstellnut als Stellpartner der Stößelmittel sorgt dann auch für eine (zumindest abschnittsweise) axiale Rückstellung der Stößeleinheit, nämlich dadurch, dass ein erhöhter Nutengrund eine rückstellende Bewegung induziert.From the prior art generic electromagnetic actuators are well known; that's how it describes them DE 201 14 466 U1 the applicant the structural design of such, used for camshaft adjustment actuator. When energizing a stationary coil unit, a relative to this and a stationary core unit movable armature unit is driven. An attached to the armature unit, elongated and end designed to engage in a camshaft adjustment of the adjusting ram unit is brought by the armature unit in an engaged position and causes in this the desired camshaft adjustment. The adjustment groove as an adjusting partner of the plunger means then also ensures (at least in sections) axial return of the plunger unit, namely in that a raised groove bottom induces a restoring movement.

In der praktischen Realisierung der beschriebenen gattungsbildenden Technologie kommt es neben zuverlässiger, betriebssicherer Großserientauglichkeit vor allem auf die Dynamik und die Stellkraft der Anker- bzw. der Stößelbewegung an. So ist es wichtig, dass die Stößel eines relativ kurzen (durch den Stellpartner vorgegebenen) Zeitfensters von der Ausgangsstellung in die Eingriffsstellung gebracht werden kann, was hohe Magnetkräfte (zum einen beim Überwinden permanentmagnetischer Haltekräfte der Ankereinheit am Kernbereich, zum anderen zum Erreichen einer hohen Ankerbeschleunigung) erfordert. Hinzu kommt der Umstand, dass bei der gattungsbildend herangezogenen Technologie die Abstoßungskraft (und damit die auf die Ankereinheit wirkende Beschleunigungskraft) die Rückstellkraft zum Zurückführen der Ankereinheit über den gesamten wirksamen Arbeitshub wirken muss; lange Hübe führen dann jedoch, insbesondere in Verbindung mit hohen beschleunigten Massen, zu einer hohen mechanischen Belastung der Bauteile, wiederum mit dem Erfordernis entsprechend robusterer Auslegung der Baugruppen. Das Ergebnis ist unerwünscht hoher (und kostenträchtiger) Aufwand bei den für die Großserie konzipierten Stellvorrichtungen. Schließlich sind ergänzend Alterungs- und Temperatureffekte, insbesondere bei den ankerseitig üblicherweise vorgesehenen Permanentmagnetmitteln, zu berücksichtigen, welche ergänzende Auslegungsreserven in der konkreten Realisierung erfordern.In the practical realization of the generic type technology described above, in addition to reliable, reliable mass production suitability, it is above all the dynamics and the actuating force of the armature or plunger movement. So it is important that the plunger of a relatively short (predetermined by the control partner) time window can be brought from the initial position into the engaged position, which is high Magnetic forces (on the one hand when overcoming permanent magnetic holding forces of the armature unit at the core area, on the other hand to achieve a high anchor acceleration) requires. Added to this is the fact that in the generic technology used the repulsion force (and thus acting on the armature unit acceleration force) must act the restoring force for returning the armature unit over the entire effective stroke; However, long strokes then lead, in particular in conjunction with high accelerated masses, to a high mechanical loading of the components, again with the requirement of a correspondingly more robust design of the assemblies. The result is undesirably high (and costly) overhead for the mass-produced actuators. Finally, aging and temperature effects, in particular in the case of the permanent magnet means usually provided on the armature side, must be taken into account, which require additional design reserves in the concrete realization.

Aus der DE 10 2012 101 619 A1 der Anmelderin ist eine elektromagnetische Stellvorrichtung bekannt, welche radial-seitlich an den Ankerstößel angreifende Rastmittel aufweist. Diese Rastmittel ermöglichen es, die Dynamik der Anker- und Stößelbewegung zu erhöhen, indem erst nach dem Überschreiten einer vorbestimmten Stellkraft die Rastmittel auslösen und so innerhalb verkürzter Stellzeit die Stellbewegung erfolgt. Allerdings besteht auch hier der oben diskutierte Nachteil, dass prinzipiell die Stellkraft über den gesamten wirksamen Stellhub der kombinierten Anker- und Stößeleinheit erzeugt werden muss, wie auch die Rückstellung entgegengesetzt des gesamten Hubes zu erfolgen hat. Entsprechend entstehen prinzipiell dieselben erhöhten (und aus den oben diskutierten Gründen nachteiligen) Dimensionierungserfordernisse wie beim generischen, gattungsbildenden Stand der Technik.From the DE 10 2012 101 619 A1 the applicant is an electromagnetic actuator known, which has radially-laterally engaging on the armature plunger locking means. These latching means make it possible to increase the dynamics of the armature and plunger movement, by triggering the latching means only after exceeding a predetermined force and thus the adjustment movement takes place within a shortened positioning time. However, there is also the disadvantage discussed above that, in principle, the actuating force must be generated over the entire effective actuating stroke of the combined armature and tappet unit, as well as the provision must be made opposite the entire stroke. Accordingly, in principle, the same increased (and disadvantageous for the reasons discussed above) sizing arise as in the generic, generic prior art.

Aufgabe der vorliegenden Erfindung ist es daher, bei verbessertem (insbesondere beschleunigtem und vergleichmäßigtem) Stellverhalten der Stößelmittel die Erfordernisse an Magnetkraft und Magnethub der Ankereinheit zu verringern, damit potenziell die Baugröße einer gattungsgemäßen elektromotorischen Stellvorrichtung (sowohl in radialer, als auch potenziell in axialer Richtung) zu verringern und so eine Vorrichtung zu schaffen, welche günstige Dynamikeigenschaften mit einem vergleichsweise langen wirksamen Arbeitshub der Stößelmittel kombiniert.The object of the present invention is therefore, with improved (in particular accelerated and gleichmäßigtem) control behavior of the plunger means to reduce the requirements of magnetic force and magnet arm of the armature unit, thus potentially the size of a generic electromotive actuator (both in the radial, and potentially in the axial direction) to reduce and thus to provide a device which combines favorable dynamic properties with a comparatively long effective working stroke of the plunger means.

Die Aufgabe wird durch die elektromagnetische Stellvorrichtung mit den Merkmalen des Hauptanspruchs gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen beschrieben. Zusätzlicher Schutz im Rahmen der Erfindung wird durch die Verwendung der erfindungsgemäßen elektromagnetischen Stellvorrichtung im Rahmen eines Nockenwellen-Verstellsystems beansprucht, wobei eine Nockenwellen-Verstelleinheit eines Verbrennungsmotors eine Verstellnut als Stellpartner zum Eingreifen durch die erfindungsgemäßen Stößelmittel anbietet.The object is achieved by the electromagnetic actuator with the features of the main claim. Advantageous developments of the invention are described in the subclaims. Additional protection within the scope of the invention is claimed by the use of the electromagnetic actuator according to the invention in the context of a camshaft adjusting system, wherein a camshaft adjusting unit of an internal combustion engine offers an adjusting groove as an adjusting partner for engagement by the ram means according to the invention.

In erfindungsgemäß vorteilhafter Weise ist, im Gegensatz zum Stand der Technik, die Ankereinheit relativ zu den Stößelmitteln bewegbar vorgesehen, so dass die Ankereinheit zwar (bevorzugt entlang ihres Ankerhubs) die Stößelmittel antreiben und mitnehmen kann, die relativ zur Ankereinheit bewegbaren Stößelmittel zusätzlich jedoch einen Stößelhub, bewirkt durch die erfindungsgemäßen Federmittel, ausführen können, welcher erfindungsgemäß größer als der Ankerhub selbst ist. Erfindungsgemäß wirkt die axial gekoppelte Anordnung aus Ankereinheit und Stößelmitteln zusammen mit mantelseitig an die Stößelmittel angreifenden Krafteintragsmitteln in Form des erfindungsgemäßen Druckkörpers, welcher sowohl mit dem Rampen- bzw. Konusabschnitt an den Stößelmitteln, als auch mit den Stößelabschnitten größeren bzw. kleineren Durchmessers jeweils benachbartem Rampen- bzw. Konusabschnitt zusammenwirken kann. Konkret ist diese Anordnung so ausgelegt und dimensioniert, dass die Ankereinheit durch ihre Ankerbewegung beim Durchführen des Ankerhubs die Stößelmittel entlang der Bewegungsrichtung mitnimmt, wobei, gegen die Krafteinwirkung des (mindestens einen, bevorzugt in Mehrzahl radial verteilt vorgesehenen) Druckkörpers, die Stößelmittel soweit vorgeschoben werden, bis der Konus bzw. die Rampe (bezogen auf den/die Druckkörper) überwunden ist. Der weitere Vorschub geschieht dann durch Expansion der erfindungsgemäßen Federmittel (wobei diese bereits auch schon die Ankerbewegung um den Ankerhub unterstützt haben). Im Ergebnis führt damit die kombinierte Stellwirkung sowohl der Ankermittel, als auch der Federmittel, auf die Stößelmittel zu einem wirksamen Stößelhub, welcher größer ist als der eigentliche Ankerhub; in praktischen Ausgestaltungen der Erfindung mindestens um den Faktor 1,5, weiter bevorzugt mindestens um den Faktor 2,5.In an advantageous manner according to the invention, in contrast to the prior art, the armature unit provided movable relative to the plunger means, so that the armature unit (preferably along its armature stroke) drive and can take along the plunger means, but the plunger means movable relative to the armature unit additionally a plunger stroke caused by the spring means according to the invention, can perform, which is inventively larger than the armature stroke itself. According to the invention, the axially coupled arrangement of armature unit and plunger means cooperates with force application means acting on the shell side on the plunger means in the form of the pressure body according to the invention, which has adjacent ramps both with the ramp or cone section on the plunger means and with the plunger sections of larger or smaller diameter - or cone section cooperate can. Specifically, this arrangement is designed and dimensioned such that the armature unit entrains the plunger means along the direction of movement during its armature movement, whereby the plunger means are advanced as far as the (at least one, preferably radially predominantly distributed) pressure body until the cone or ramp (related to the / the pressure body) is overcome. The further feed then happens by expansion of the spring means according to the invention (which have already already supported the armature movement to the armature stroke). As a result, so that the combined action of both the anchor means, as well as the spring means, on the plunger means to an effective ram stroke, which is greater than the actual armature stroke; in practical embodiments of the invention, at least a factor of 1.5, more preferably at least a factor of 2.5.

Vorteilhafte Konsequenz ist, dass die erfindungsgemäße Stellvorrichtung auf einen wesentlich geringeren Ankerhub dimensioniert werden kann (mit entsprechenden Vorteilen der Mechanik und des Bauvolumens), relativ zu einem erreichbaren Stellhub.An advantageous consequence is that the adjusting device according to the invention can be dimensioned to a much smaller armature stroke (with corresponding advantages of the mechanics and the construction volume), relative to an achievable control stroke.

Der erfindungsgemäße Rampen- bzw. Konusabschnitt wirkt sich gleichermaßen vorteilhaft bei der Rückstellung der Stellvorrichtung bzw. der Stößelmittel in die Ausgangsstellung aus. So ist es nämlich erfindungsgemäß ausreichend, wenn die Stößelmittel aus der Eingriffsstellung (etwa durch den in der bevorzugten Verwendungsform "Nockenwellenverstellung" vorgesehenen Eingriff in die Verstellnut) lediglich so weit entgegen der Bewegungsrichtung zurückgestellt werden, bis - axial - der/die Druckkörper den Rampen- bzw. Konusabschnitt erreicht/en. Zu diesem Zeitpunkt würde dann nämlich die mantelseitige Krafteinwirkung auf den Rampen- bzw. Konusabschnitt zu einer weiteren Rückstellung bzw. Kraftbeaufschlagung der Stößelmittel in Richtung auf die Ausgangsstellung führen, ohne dass dieser (gegenüber dem Stellpartner zusätzlich) Rückstellhub weiteren Kontakt mit dem Stellpartner erfordert oder auf sonstige Weise extern angetrieben werden muss. Wiederum ist vorteilhafte Wirkung auch für die Rückstellbewegung, dass die Ankereinheit selbst einen Ankerhub kleiner als der Stößelhub aufweisen muss.The ramp or cone section according to the invention has an equally advantageous effect on the return of the adjusting device or the plunger means to the starting position. Thus, according to the invention, it is sufficient if the plunger means are reset from the engagement position (for example, by the engagement in the adjustment groove provided in the preferred use form "camshaft adjustment") only so far against the direction of movement, until - axially - the pressure body (s) reaches the ramp. or cone section reaches / s. At that time, namely, the shell-side force acting on the ramp or cone section to a further provision or force application of the plunger means in the direction of the starting position lead, without this (in addition to the adjusting partner) Rückstellhub further contact with the control partner requires or otherwise driven externally. Again, advantageous effect also for the return movement, that the anchor unit itself must have an armature stroke smaller than the ram stroke.

Während es im Rahmen bevorzugter Weiterbildungen der Erfindung bevorzugt ist, den Druckkörper als Kugel bzw. kugelförmigen Abschnitt eines abweichend gestalteten Druckkörpers auszugestalten, sind auch andere Varianten denkbar; weiterbildend vorteilhaft ist es gleichwohl, den Druckkörper, weiter bevorzugt vorgespannt durch die Vorspannkraft einer bevorzugt radial zur Bewegungsrichtung ausgerichteten Druckfeder, in Mehrzahl und um einen Umfang der Stößelmittel verteilt herum anzuordnen, so dass insoweit eine zuverlässige Beeinflussung der Stößelbewegung durch diese/n Druckkörper erfolgen kann.While it is preferred in the context of preferred developments of the invention to design the pressure body as a ball or spherical portion of a differently shaped pressure body, other variants are conceivable; It is nevertheless advantageous to arrange the pressure body, more preferably pretensioned by the pretensioning force of a compression spring which is preferably oriented radially to the direction of movement, in a plurality and around a circumference of the plunger means, so that a reliable influencing of the plunger movement by these pressure bodies can take place ,

Sofern ein Federkraftvektor einer den Druckkörper vorspannenden (Druck-)Feder eine Radialkomponente besitzt, ist eine konkrete Anordnung der Feder beliebig und kann sich nach den Gegebenheiten im umgebenden Gehäuse richten; dies gilt auch für die konkrete Ausgestaltung einer Feder.If a spring force vector of the pressure body biasing (pressure) spring has a radial component, a concrete arrangement of the spring is arbitrary and may depend on the circumstances in the surrounding housing; This also applies to the specific design of a spring.

Im Rahmen konkreter und bevorzugter Ausgestaltungen der Erfindung ist die Geometrie des Rampen bzw. Konusabschnittes wichtig; in der praktischen Realisierung hat es sich als bevorzugt herausgestellt, eine Erstreckung des Rampen- bzw. Konusabschnittes vorzusehen, welcher größer als eine (maximale) axiale Erstreckung des Druckkörpers, also etwa ein Kugeldurchmesser, ist. Auch ist es weiterbildungsgemäß vorteilhaft, die axiale Erstreckung des Rampen- bzw. Konusabschnittes so in Beziehung zum Ankerhub zu setzen, dass durch die Ankerbewegung entlang des Ankerhubs ein Großteil des axialen Wegs des Druckkörpers entlang des Rampen- bzw. Konusabschnittes überwunden werden kann, wobei zu diesem Zweck bevorzugt der Rampen- bzw. Konusabschnitt in etwa dem Ankerhub entspricht, erfindungsgemäß weiterbildend 50% bis 150%, bevorzugt 80% bis 120%, des Ankerhubs.In the context of specific and preferred embodiments of the invention, the geometry of the ramp or cone section is important; In practical implementation, it has been found preferable to provide an extension of the ramp or cone section, which is greater than a (maximum) axial extent of the pressure hull, that is about a ball diameter. It is also advantageous in terms of further development to set the axial extent of the ramp or cone section in relation to the armature stroke in such a way that, as a result of the armature movement along the armature stroke, a major part of the axial travel of the pressure body along the armature Rampen- or cone section can be overcome, for which purpose preferably the ramp or cone section corresponds approximately to the armature stroke, according to the invention further developing 50% to 150%, preferably 80% to 120% of the anchor stroke.

Gleichermaßen nützlich ist es im Rahmen von Weiterbildungen der Erfindung, einen Steigungswinkel des Rampen- bzw. Konusabschnitts (etwa gemessen im Längsschnitt relativ zur Bewegungs-Längsachse) im Bereich zwischen 20° und 60°, bevorzugt zwischen 30° und 50°, vorzusehen.Equally useful in the context of developments of the invention, a pitch angle of the Rampen- or cone section (as measured in longitudinal section relative to the longitudinal axis of movement) in the range between 20 ° and 60 °, preferably between 30 ° and 50 ° to provide.

In konstruktiv besonders günstiger Weise ist es weiterbildungsgemäß vorgesehen, die Federmittel, weiter bevorzugt realisiert als Druck- und/oder Spiralfeder, in einem (hohlzylindrischen) Innenbereich der radialsymmetrisch ausgebildeten Stößelmittel vorzusehen; zu diesem Zweck können die Stößelmittel etwa einen hohlzylindrischen Innenraum und/oder einen inneren Ringabsatz aufweisen. Anderenends würden sich dann die Federmittel etwa an einem Abschnitt eines die Stößelmittel führenden Gehäuses abstützen können, so dass erfindungsgemäß vorteilhaft die Federmittel ihren Beitrag zur Beschleunigung der Stößeleinheit leisten können, wobei weiterbildungsgemäß die Ankereinheit nach wie vor und in ansonsten bekannter Weise Permanentmagnetmittel aufweisen kann, alternativ aber auch auf andere Weise relativ zu der stationären Kerneinheit elektromagnetisch betätigbar ist.In a structurally particularly favorable manner, it is provided according to further development, the spring means, more preferably realized as a pressure and / or coil spring, in a (hollow cylindrical) interior of the radially symmetrical tappet means provided; For this purpose, the plunger means may have approximately a hollow cylindrical interior and / or an inner annular shoulder. At the other end, the spring means would then be able to support, for example, a portion of a housing guiding the plunger means, so that according to the invention the spring means can make their contribution to accelerating the plunger unit, wherein the armature unit can continue to have permanent magnet means as before and in otherwise known manner, alternatively but also electromagnetically operable in other ways relative to the stationary core unit.

Besonders bevorzugt ist es im Rahmen von Weiterbildungen der Erfindung zudem, die Ankereinheit (bzw. den im Rahmen der Stellvorrichtung bewirkten elektromagnetischen Antrieb der Ankereinheit) monostabil auszugestalten, d.h. lediglich eine Anker-Ausgangsstellung als einzige stabile Endstellung vorzusehen, wobei dann bei Bestromung der Spulenmittel zwar die Ankereinheit um den Anker bewegt wird, nach Beendigung der Bestromung jedoch die Ankereinheit in die Anker-Ausgangsstellung zurückfällt. Vorteilhaft im Zusammenwirken mit den Stößelmitteln ist diese Konfiguration dadurch, dass die Ankereinheit nach dem initialen Antreiben der Stößelmittel keinen Beitrag zum weiteren Vorschub der Stößelmittel leistet (dies wird vielmehr durch die Federmittel übernommen) während dann beim Zurückführen, insbesondere auch durch das Zusammenwirken zwischen Druckkörper und Rampen- bzw. Konusabschnitt, kein zusätzliches Zurückführen bzw. Mitnehmen der Ankereinheit in die Ausgangsstellung notwendig ist.It is particularly preferred in the context of developments of the invention also, the armature unit (or caused in the actuator electromagnetic drive of the armature unit) monostable to design, ie only provide an anchor initial position as a single stable end position, in which case while energizing the coil means though the armature unit is moved around the armature, after completion of the energization, however, the armature unit falls back into the armature's starting position. This configuration is advantageous in cooperation with the plunger means in that the armature unit after the initial driving of the plunger means makes no contribution to further advancement of the plunger means (this is rather taken over by the spring means) while then returning, in particular by the interaction between the pressure body and Rampen- or cone section, no additional return or take along the anchor unit is necessary in the starting position.

Im Ergebnis ist durch die vorliegende Erfindung eine Vorrichtung geschaffen, welche eine wirksame Hublänge existierender, gattungsgemäßer Stellvorrichtungen deutlich verlängert, ohne gleichermaßen größere bzw. voluminösere Magnetanordnungen zu erfordern. Entsprechend ergeben sich insbesondere für den bevorzugten Anwendungskontext "Nockenwellenverstellung" signifikante Vorteile, nicht zuletzt im Herstellungsaufwand und in der Ersparnis benötigten Einbauraums. Die vorliegende Erfindung ist jedoch nicht auf diesen Anwendungskontext beschränkt, sondern eignet sich vielmehr auch für beliebige andere Stellanwendungen, bei welchen mit begrenzten elektromagnetischen Mitteln lange Stellhübe realisiert werden sollen.As a result, an apparatus is provided by the present invention which significantly prolongs effective stroke length of existing generic actuators without requiring equally larger or bulkier magnet assemblies. Accordingly, there are significant advantages, in particular for the preferred application context "camshaft adjustment", not least in the manufacturing effort and in the space required installation space. However, the present invention is not limited to this application context, but rather is also suitable for any other actuating applications in which long staging strokes are to be realized with limited electromagnetic means.

Weitere Vorteile, Merkmale und Einzelheiten der vorliegenden Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der einzigen Figur; diese zeigt in:

Fig. 1
eine schematische Längsschnittdarstellung der elektromagnetischen Stellvorrichtung gemäß einer ersten bevorzugten Ausführungsform der Erfindung, symbolisch geteilt entlang der vertikalen Symmetrie- und Bewegungsachse in eine zurückgezogene Ausgangsstellung (rechts) und einen Eingriffszustand (links) relativ zu einer Nockenwellen-Schaltkulisse als Eingriffspartner.
Further advantages, features and details of the present invention will become apparent from the following description of preferred embodiments and with reference to the single figure; this shows in:
Fig. 1
a schematic longitudinal sectional view of the electromagnetic actuator according to a first preferred embodiment of the invention, symbolically divided along the vertical axis of symmetry and movement in a retracted initial position (right) and an engaged state (left) relative to a camshaft shift gate as engagement partner.

In der Längsnutdarstellung der Fig. 1 zeigt das Bezugszeichen 10 symbolisch eine Ankereinheit mit einem langgestreckten Ankerstößel 12 sowie einem relativ dazu verbreiterten Ankerkörper 14. Durch (in der Fig. nicht gezeigte) bestrombare Spulenmittel ist in ansonsten bekannter Weise die Ankereinheit 10 relativ zu einer stationären Kerneinheit (nicht gezeigt) bewegbar, zwischen einer Anker-Ausgangsstellung (Fig. 1, rechts) und einer Anker-Vorschubstellung (Fig. 1, linke Hälfte). In einer praktischen Realisierung liegt ein typischer Ankerhub im Bereich zwischen 1 und 1,5 mm bei einem effektiven Hub der Stößelmittel von ca. 4 mm.In the Längsnutdarstellung the Fig. 1 the reference numeral 10 symbolically shows an armature unit with an elongated armature tappet 12 and an armature body 14 which is widened relative to it. By means of an armature coil (not shown in the figure), the armature unit 10 is movable in an otherwise known manner relative to a stationary core unit (not shown), between an anchor home position ( Fig. 1 , right) and an armature feed position ( Fig. 1 , left half). In a practical implementation, a typical armature stroke is in the range between 1 and 1.5 mm with an effective stroke of the plunger means of about 4 mm.

Wie die Fig. 1 schematisch weiter verdeutlicht, greift der Ankerstößelabschnitt 12 innen auf eine Stößeleinheit (Stößelmittel) 16, welche in einem umgebenden Stößelgehäuse 18 geführt ist. Wie die Längsschnittdarstellung der Fig. 1 erkennen lässt, ist in Richtung auf die Ankereinheit 10 die Stößeleinheit 16 bodenseitig zum Aufnehmen des Ankerstößelabschnitts 12 geöffnet; dieser ist so dimensioniert, dass er in der Anker-Ausgangsstellung (Fig.1, rechte Hälfte) einen - kleinen - Abstand vom Stößel einhält und erst bei Vorschub den Stößel 16 dann entlang der Bewegungsrichtung (in der Figurenebene der Fig. 1 abwärts) mitnimmt.As the Fig. 1 schematically further illustrated, engages the anchor tappet portion 12 inside of a plunger unit (plunger means) 16, which is guided in a surrounding plunger housing 18. Like the longitudinal section of the Fig. 1 can be seen, in the direction of the armature unit 10, the plunger unit 16 is open on the bottom side for receiving the armature tappet portion 12; this is dimensioned so that it is in the anchor position ( Fig.1 , right half) a - small - distance from the plunger complies and only at feed the plunger 16 then along the direction of movement (in the plane of the figure Fig. 1 down).

Zusätzlich an einen Boden bzw. einen Ringabsatz 20 der Stößeleinheit 16 angreifend ist eine Spiralfeder 22 gezeigt, welche sich anderenends von einem Ringboden 24 des Stößelgehäuses 18 abstützt. In der rechten Hälfte der Fig. 1, insoweit entsprechend der Ausgangsstellung der Stößelmittel 16, ist entsprechend die Spiralfeder 22 komprimiert und übt eine maximale Vorspannung auf die Stößeleinheit 16 in abwärts gerichteter Bewegungsrichtung aus.In addition to a bottom or an annular shoulder 20 of the plunger unit 16 attacking a coil spring 22 is shown, which is supported at the other end of a ring bottom 24 of the plunger housing 18. In the right half of the Fig. 1 As far as corresponding to the initial position of the plunger means 16, the coil spring 22 is correspondingly compressed and exerts a maximum bias on the plunger unit 16 in the downward direction of movement.

Die Stößeleinheit 16 weist, in Richtung auf die Ankereinheit 10, einen Stößelabschnitt 26 größeren Außendurchmesser auf; über einen Konusabschnitt 28 verjüngt sich dieser (größere) Außendurchmesser in einem eingriffsseitigen vorderen Stößelabschnitt 30 verminderten Außendurchmesser. Wie die Längsschnittansicht erkennen lässt, erstreckt sich der Konusabschnitt 28 über eine axiale Länge von ca. 1,2 mm bei einem Winkel bezogen auf die vertikale Bewegungsachse von ca. 25°. Insoweit entspricht die axiale Erstreckung (axiale Länge) des Konusabschnitts 28 dem Ankerhub, zuzüglich des (spielbehafteten) Abstands zwischen einem Eingriffsende 34 der Stößeleinheit und dem Stellpartner im Nicht-Eingriffszustand.The ram unit 16 has, in the direction of the armature unit 10, a tappet portion 26 larger outside diameter; via a cone section 28, this (larger) outer diameter tapers in an engagement-side front tappet section 30 of reduced outer diameter. As the longitudinal sectional view reveals, the cone section 28 extends over an axial length of about 1.2 mm at an angle with respect to the vertical axis of motion of about 25 °. In that regard, the axial extent (axial length) of the cone portion 28 corresponds to the armature stroke, plus the (gap) distance between an engagement end 34 of the plunger unit and the actuator in the disengaged state.

Wie die Fig. 1 zusätzlich erkennen lässt, greifen Druckkörper 32 in Form von um den Umfang der Stößeleinheit 16 herum verteilt angeordneter Kugeln auf die Mantelfläche der Stößeleinheit; diese Kugeln 32 sind durch eigene, sich horizontal (und damit radial zu der Bewegungs-Längsachse) erstreckende Druckfedern 33 vorgespannt.As the Fig. 1 can additionally recognize, grip pressure body 32 in the form of distributed around the circumference of the plunger unit 16 around balls on the lateral surface of the plunger unit; These balls 32 are biased by their own, horizontally (and thus radially to the longitudinal movement axis) extending compression springs 33.

Eingriffsseitig, d.h. der Ankereinheit 10 entgegensetzt, bildet die Stößeleinheit 16 den Eingriffsabschnitt (Eingriffsende) 34 aus, welcher bemessen ist, mit einer Schaltnut 36 einer exemplarisch als Stellpartner gezeigten Schaltkulisse 38 eines Nockenwellen-Verstellsystems zusammenzuwirken; der Doppelpfeil 40 verdeutlicht die Nutentiefe im gezeigten Beispiel von ca. 3,7 mm, welche durch den Stößelhub (hier ca. 4 mm) abgedeckt wird.Engaging side, i. opposes the armature unit 10, the plunger unit 16 forms the engagement portion (engagement end) 34, which is dimensioned to cooperate with a shift groove 36 of an exemplary shown as a control partner shift gate 38 of a camshaft adjustment system; the double arrow 40 illustrates the groove depth in the example shown by about 3.7 mm, which is covered by the ram stroke (here about 4 mm).

Der Betrieb der in Fig. 1 gezeigten Vorrichtung ist wie folgt:

  • Aus der Ausgangslage der Ankereinheit (rechte Hälfte der Fig. 1) erfolgt durch Bestromung der (nicht gezeigten) Spulenmittel zunächst eine Bewegung der Ankereinheit (bestehend aus dem Ankerkörper 14 und dem direkt und fest ansitzenden, alternativ (permanent-)magnetisch haftend ansitzenden Ankerstößel 12) entlang der Bewegungsrichtung, also in Fig. 1 abwärts; der Ankerhub liegt im Bereich zwischen ca. 1 und 1,5 mm. Bei Erreichen des Widerlagers 20 der Stößeleinheit 16 wird diese entlang der Bewegungsrichtung mitgenommen; gleichzeitig schiebt sich der Konusabschnitt 28 in Richtung abwärts entlang der horizontal feststehenden kugelförmigen Druckkörper 32, bis diese auf dem (oberen) zylindrischen Mantelabschnitt 26 der Stößeleinheit liegen. Während die sich entspannende Druckfeder 22 bereits die Ankerbewegung unterstützt hat und insoweit eine zusätzliche, abwärtsgerichtete Stellkraft auf die Stößeleinheit 16 ausgeübt hat, übernimmt die Druckfeder 22 vollständig den weiteren, abwärtsgerichteten Vorschub der Stößeleinheit 16, sobald die Ankereinheit ihren Anschlagszustand am Gehäuse 18 erreicht (Fig. 1, linker Bereich für den Ankeranschlag); während die Feder 22 die Stößeleinheit weiter abwärts führt, trennt sich der Ankerstößelabschnitt 12 von der Stößeleinheit 10.
Operation of in Fig. 1 shown device is as follows:
  • From the initial position of the anchor unit (right half of Fig. 1 ) is carried out by energizing the coil means (not shown), first a movement of the armature unit (consisting of the anchor body 14 and the directly and firmly ansitzenden, alternatively (permanently) magnetically adhering anchoring anchor plunger 12) along the direction of movement, ie in Fig. 1 down; the armature stroke is in the range between approx. 1 and 1.5 mm. Upon reaching the abutment 20 of the plunger unit 16, this is taken along the direction of movement; At the same time, the cone section 28 slides in the downward direction along the horizontally fixed spherical pressure body 32, until they lie on the (upper) cylindrical shell portion 26 of the plunger unit. While the relaxing compression spring 22 has already supported the armature movement and so far has exerted an additional, downward force on the plunger unit 16, the compression spring 22 completely takes over the further, downward feed of the plunger unit 16 as soon as the armature unit reaches its stop state on the housing 18 ( Fig. 1 left armature stop area); while the spring 22 continues to lower the ram unit, the armature tappet portion 12 separates from the ram unit 10.

Der linke Bereich der Fig. 1 zeigt den vollständig ausgeschobenen Zustand des Ankerstößels 16 aus dem Gehäuse 18. Die Stößeleinheit 16 hat einen Gesamthub von ca. 4 mm vollführt und greift in diesem Zustand in die Nut 36 des Stellpartners 38 ein. Bei Rotation der Baugruppe 38 erfolgt in ansonsten bekannter Weise die Nockenwellenverstellung.The left area of the Fig. 1 shows the fully ejected state of the armature plunger 16 from the housing 18. The plunger unit 16 has a total stroke of about 4 mm performs and engages in this state in the groove 36 of the adjusting partner 38 a. Upon rotation of the assembly 38, the camshaft adjustment takes place in an otherwise known manner.

Die Stellnut 36 bewirkt auch die Rückstellung des Stößels 16 entlang eines ersten Rückstell-Hubabschnitts; konkret führt eine sich verringernde Nuttiefe (bei Rotation der Kulisse 38) dazu, dass die Stößeleinheit 16 in der Rückstellrichtung (d.h. in der Figurenebene der Fig. 1 aufwärts) geschoben wird. Die gezeigte Vorrichtung ist dabei so dimensioniert, dass diese Rückstellung entlang des ersten Rückstellhubs soweit axial erfolgt, bis die auf die zylindrische Mantelfläche 26 greifenden Kugeln 32 den Anfang des Konusabschnittes 28 (wirkend als Rampe) erreichen. Zu diesem Zeitpunkt führt dann die radiale Kraftbeaufschlagung der Kugeln 32 als Druckkörper dazu, dass entlang der Konusfläche die Rückstellbewegung in Richtung auf die Ausgangsstellung fortgeführt wird, wobei der Konus insoweit einen sich an den ersten Rückstellhub der Nut anschließenden zweiten Rückstellhub, bis in die in der Fig. 1 rechts gezeigte Ausgangsposition, bestimmt. Da die Ankereinheit 10 in der vorbeschriebenen Weise monostabil ausgeführt ist, muss die Stößeleinheit 16 bei diesem Rückstellvorgang nicht noch zusätzlich die Ankereinheit 10 mit zurückstellen (etwa durch Mitnahme des Abschnitts 12), vielmehr erfolgte unmittelbar nach dem Bestromungsende bereits beim Herausführen des Stößels 16 ein Zurückfallen der Ankereinheit 10 in ihre monostabile Endposition (Fig. 1, rechts). Alternativ kann auch eine bistabile Ausgestaltung, etwa mittels eines permanentmagnetisch realisierten Ankerkörpers 14, sinnvoll sein, insbesondere auch im Hinblick auf eine damit realisierbare (magnetfelddetektierte) Positions-, Bewegungs- und/oder Rückstellerfassung.The adjusting groove 36 also causes the return of the plunger 16 along a first return stroke section; Concretely, a decreasing groove depth (upon rotation of the gate 38) causes the plunger unit 16 to move in the return direction (ie in the plane of the figure) Fig. 1 pushed upward). The device shown here is dimensioned such that this provision takes place axially as far along the first return stroke until the balls 32 engaging on the cylindrical lateral surface 26 reach the beginning of the cone section 28 (acting as a ramp). To this Time then leads the radial application of force to the balls 32 as a pressure body to that along the conical surface, the return movement is continued in the direction of the starting position, the cone so far a subsequent to the first return stroke of the groove second return stroke, to the in the Fig. 1 right starting position, determined. Since the anchor unit 10 is designed monostable in the manner described above, the plunger unit 16 in this return operation does not additionally reset the anchor unit 10 with (about by entrainment of the section 12), but took place immediately after the Bestromungsende already when taking out the plunger 16 is a falling back the anchor unit 10 in its monostable end position ( Fig. 1 , right). Alternatively, a bistable design, for example by means of a permanently magnetically realized anchor body 14, be useful, especially with regard to a so realized (magnetic field detected) position, motion and / or reset device.

Claims (12)

  1. Electromagnetic actuating device comprising
    an armature unit (10) which is able to be driven by supplying current to stationary coil means by an armature stroke in an axial direction of movement,
    plunger means (16) which are assigned to the armature unit, which are configured on the end side for cooperating with an external actuating partner and which are movable by a plunger stroke from an initial position into an engagement position in the direction of movement
    and spring means (22) which pretension the plunger means in the direction of movement,
    characterised in that the plunger means, which are movably guided relative to the armature unit, on the shell side comprise a ramp section and/or cone-shaped section (28) between a plunger portion of larger diameter (26) on the armature side and a plunger portion (30) with a smaller diameter,
    a pressure body (32), which is contained under pretensioning in a housing portion (18) guiding the plunger means, cooperates on the shell side with the ramp section and/or cone-shaped section
    and the ramp section and/or cone-shaped section is provided on the plunger means such that the pressure body, when the coil unit is not supplied with current and/or when the armature unit is not driven, by the action of force on the shell side on the ramp section and/or cone-shaped section, returns the plunger means counter to the pretensioning of the spring means in the direction of the initial position, in particular into the initial position,
    wherein the armature stroke is smaller than the plunger stroke.
  2. Device according to Claim 1, characterised in that the pressure body is configured as a ball (32) or a body comprising a spherical segment and is preferably provided in the form of a plurality of pressure bodies arranged so as to be distributed around a periphery of the plunger means.
  3. Device according to Claim 1 or 2, characterised in that the ramp section and/or cone-shaped section (28) has an extent in the axial direction of movement which is greater than a diameter or an axial extent of the pressure body and/or is between 50% and 150%, preferably between 80% and 120%, of the armature stroke.
  4. Device according to one of Claims 1 to 3, characterised in that the ramp section and/or cone-shaped section (28) is inclined along the longitudinal section by an angle (α) of between 20° and 60°, preferably of between 30° and 40°, relative to the longitudinal axis of the direction of movement.
  5. Device according to one of Claims 1 to 4, characterised in that the plunger stroke is at least 1.5 times, preferably at least 2.5 times, the armature stroke.
  6. Device according to one of Claims 1 to 5, characterised in that the plunger means (16), which are implemented radially symmetrically about the longitudinal axis of movement in the direction of movement, comprise an internal widening for receiving the spring means configured as a spiral spring and/or an internal shoulder providing a stop (20) for the spring means, in particular an annular shoulder.
  7. Device according to Claim 6, characterised in that the spring means which are configured as a compression spring and/or spiral spring (22) are supported at one end on the plunger means (16) and at the other end on a portion (24) of the housing (18) guiding the plunger means.
  8. Device according to one of Claims 1 to 7, characterised in that the armature unit is configured to be monostable such that after germinating the supply of current the armature unit drops back into an armature initial position.
  9. Device according to Claim 8, characterised in that the armature unit is dimensioned and designed such that in the armature initial position no mechanical contact exists with the plunger means.
  10. Device according to one of Claims 1 to 9, characterised in that the plunger means are configured for cooperating with an actuating groove (36) as an actuating partner, such that a change in the position and/or depth of the actuating groove may effect a movement of the plunger means in a restoring direction opposing the direction of movement,
  11. Device according to one of Claims 1 to 10, characterised in that the armature unit comprises permanent magnet means which are configured for cooperating with means for detecting the position, movement and/or restoring of the armature unit.
  12. Cam shaft adjusting system comprising the electromagnetic actuating device according to one of Claims 1 to 11, and an actuating groove (36) as an actuating partner for engagement by the cam shaft adjusting unit (38) of an internal combustion engine, said cam shaft adjusting unit providing plunger means,
    wherein the actuating groove and the plunger means are configured and axially aligned relative to one another such that the actuating groove may perform a first restoring stroke onto the plunger means counter to the direction of movement and the first restoring stroke may move the pressure body onto the ramp section and/or cone-shaped section in order to bring about an axially aligned, preferably a subsequent, second restoring stroke by the action of force on the shell side.
EP14828454.0A 2013-12-23 2014-12-18 Electromagnetic actuating mechanism Active EP3087575B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013114830.1A DE102013114830A1 (en) 2013-12-23 2013-12-23 Electromagnetic actuator
PCT/EP2014/078547 WO2015097068A1 (en) 2013-12-23 2014-12-18 Electromagnetic actuating mechanism

Publications (2)

Publication Number Publication Date
EP3087575A1 EP3087575A1 (en) 2016-11-02
EP3087575B1 true EP3087575B1 (en) 2017-07-12

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EP14828454.0A Active EP3087575B1 (en) 2013-12-23 2014-12-18 Electromagnetic actuating mechanism

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US (1) US9741481B2 (en)
EP (1) EP3087575B1 (en)
CN (1) CN105830179B (en)
DE (1) DE102013114830A1 (en)
WO (1) WO2015097068A1 (en)

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CN117123981B (en) * 2023-10-26 2024-03-15 江苏快克芯装备科技有限公司 Micro-pressure device of chip suction mechanism and chip welding machine

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Also Published As

Publication number Publication date
CN105830179B (en) 2018-01-23
DE102013114830A1 (en) 2015-06-25
CN105830179A (en) 2016-08-03
WO2015097068A1 (en) 2015-07-02
US20160322146A1 (en) 2016-11-03
EP3087575A1 (en) 2016-11-02
US9741481B2 (en) 2017-08-22

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