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EP0405187B1 - Electromagnetic positioning device - Google Patents

Electromagnetic positioning device Download PDF

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Publication number
EP0405187B1
EP0405187B1 EP90110559A EP90110559A EP0405187B1 EP 0405187 B1 EP0405187 B1 EP 0405187B1 EP 90110559 A EP90110559 A EP 90110559A EP 90110559 A EP90110559 A EP 90110559A EP 0405187 B1 EP0405187 B1 EP 0405187B1
Authority
EP
European Patent Office
Prior art keywords
positioning device
armature
transmission system
control element
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90110559A
Other languages
German (de)
French (fr)
Other versions
EP0405187A1 (en
Inventor
Peter Dr.-Ing. Kreuter
Armin Dipl.-Ing. Zoschke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FEV Europe GmbH
Original Assignee
FEV Motorentechnik GmbH and 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 FEV Motorentechnik GmbH and Co KG filed Critical FEV Motorentechnik GmbH and Co KG
Priority to AT90110559T priority Critical patent/ATE95277T1/en
Publication of EP0405187A1 publication Critical patent/EP0405187A1/en
Application granted granted Critical
Publication of EP0405187B1 publication Critical patent/EP0405187B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • F01L1/182—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft
    • 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
    • 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L2001/188—Fulcrums at upper surface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/20—Control lever and linkage systems
    • Y10T74/20576—Elements
    • Y10T74/20882—Rocker arms

Definitions

  • the invention relates to an electromagnetically operating control device for at least one oscillatingly movable control element for displacement machines, in particular flat slide valves and globe valves, with two switching electromagnets, which correspond to the open and the closed switching position of at least one control element, with one arranged between the two switching electromagnets ,
  • the position of the control element determining armature, and with a spring system for oscillating force transmission to the armature between the switching positions, which is dimensioned such that the position of the equilibrium position of the armature lies between the two switching positions.
  • Such an actuator is known from DE-OS 30 24 109.
  • the control element of a displacement machine is held in the closed state by a compression spring in an actuating device of the type listed.
  • Another compression spring acts on a magnet armature interacting with the control element, so that the equilibrium position of the spring system lies in the middle or near the middle between the end positions of the movement of the magnet armature.
  • the end positions of the armature movement are each on an electrically operated switching magnet. To switch this device, one switching magnet is energized and the other switched off. Due to the force of the prestressed spring, the armature is accelerated to the equilibrium position and decelerated on its further path by the counteracting force of the other spring which then determines. Due to friction, the armature cannot reach the opposite end position. On the missing remaining path, the armature is attracted by the pulling force of the switching magnet.
  • This is also an oscillating spring mass system with an equilibrium position between two switching positions.
  • An essential feature of this system is the design of the spring system as a torsion bar spring with valve actuation via a rocker arm with a fixed transmission ratio that is connected to the torsion bar spring in a rotationally fixed manner.
  • the main goals are to minimize the moving masses of the spring-mass system and to increase the effective stroke of the poppet valve when the armature moves for standard electromagnets.
  • systems of this type achieve a reduction in size because the radial dimension of the winding window can be kept small due to the smaller air gap to be bridged. This is particularly important with regard to the use of the actuating device on displacement machines.
  • the working stroke of such an actuating device is to be dimensioned such that a sufficient opening cross-section is available for the largest mass flow occurring at the control element of a displacement machine and thus throttling is avoided.
  • operation of the actuating device at this maximum working stroke is uneconomical, since the electrical energy to be supplied for changing the position of the control element increases as a function of the stroke of the control element.
  • the reduction in the opening cross-section results in an increase in the flow speed at the control element, which contributes to the improvement of the preparation of multiphase mixtures, in particular an air-fuel mixture in internal combustion engines.
  • the executable maximum stroke of the control valve is, however, limited in the previously known types by the dimensions of the actuating device and by the predetermined positioning in the extension of the valve axis and cannot be changed.
  • US-A-1 395 851 describes a possibility of varying the rocker gear ratio by changing the position of the rocker arm axis, with the aim of achieving an improvement in efficiency by means of an opening cross section which is adapted to the respective engine power.
  • the opening and closing times of the valves can only be varied in direct dependence on one another.
  • the object of the present invention is to achieve a flexible adaptation of the actuating device to the respective operating conditions and at the same time an energy saving with the most compact possible dimensions of the actuating device and a freer arrangement of the actuating device in the receptacle, in particular in a cylinder head for an internal combustion engine.
  • an electromagnetically operating control device of the type described in the introduction by means of a variable power transmission system which interacts with the armature and at least one control element, by means of which the armature switches the at least one control element back and forth via means for changing the transmission ratio, the transmission system thus is connected to the oscillating system consisting of the spring system, the armature around the control element, that the equilibrium position of the armature is adjustable, by a common device for simultaneously changing the transmission ratio and the magnetic resistance in the magnetic circuit of one or both working magnets for setting the fall times of the armature , and to adapt the equilibrium position of the vibrating system to the new spring forces by changing the position of one or more spring base points.
  • the transmission system is designed as a hydraulic transmission which is variable in the transmission ratio.
  • the vibratory spring-mass system with compression springs on both sides of the armature is designed according to a further embodiment of the invention so that the springs or spring assemblies are divided into springs arranged on the magnet side and springs arranged on the control element.
  • a plurality of control elements cooperate with one transmission system each, with valve displacement machines each having a transmission system per valve or a common transmission system for several valves.
  • a further embodiment of the invention provides for the non-moving base point of one or more springs of the vibratable system to be adjustable.
  • the aim here is that the adjustment in the receiving housing, in particular in the cylinder head of an internal combustion engine, is arranged so that it is easily accessible, since the correct setting of the equilibrium position takes place under operating conditions.
  • this adjustment takes place either directly by shifting wedge surfaces relative to one another or via a transmission member which is designed as a rocker arm or finger follower.
  • a hydraulic compensation element is provided for the play-free actuation of the oscillating components.
  • the compensating element can be arranged at different positions within the moving components, in particular in the transmission system or in the magnet armature.
  • the hydraulic compensating element is arranged between the receptacle housing and the switching magnet assigned to the closed valve position, the axial displacement of the switching magnet compensating for the changes in length that occur in the moving components.
  • a further advantageous embodiment of the invention consists in the arrangement of the hydraulic compensating element between the mounting of the transmission element and the receiving housing or the adjusting element.
  • Another advantageous embodiment of the invention consists in the use of permanent magnets in the switching magnets.
  • Another embodiment of the invention relates to damping the armature movement shortly before reaching the end positions.
  • the base point of one of the springs or spring assemblies assigned to the oscillatory system can be adjusted according to further developments of the invention.
  • the magnetic resistance of the magnetic circuit of one or both working magnets is changed when the ratio of the transmission system changes and thus when the effective spring forces change, with the aim of changing the time between the switching off of the current Keep working magnets and the beginning of the armature movement, hereinafter called fall time, constant.
  • both the change in the magnetic resistance and the adjustment of the translation of the transmission element and the equilibrium position of the vibrating system are carried out by a common device.
  • the invention advantageously changes the switching stroke of the adjusting device and thus the effective opening cross-section of the lifting valve or flat slide valve while largely maintaining the compact dimensions of the adjusting device. Furthermore, compared to the arrangement of an actuating device in a direct extension of the shaft of the control element, an increase in the maximum stroke of the control element is possible. A further advantage is that the actuating device can be arranged around the valve stem within a radius predetermined by the transmission system, and thus greater freedom of design for the receiving housing is achieved. The invention also enables an exact adjustment of the equilibrium position of the vibrating system in the installed state, and the tracking of the equilibrium position of the vibrating system when the transmission ratio of the transmission system changes.
  • FIG. 1 shows an example of an electromagnetically operating actuating device with electromagnets 1 and 2, windings 3 and 4 and armature 5.
  • the electromagnets 1 and 2 are fixed in by a cover 6 and with the interposition of a cam ring 7 Housing 8 clamped.
  • the armature 5 is guided in a sleeve 53 and actuates a valve 12 via a rocker arm 10.
  • Pressure springs 13, 14 and 50 form the oscillating system, taking into account the transmission ratio of the rocker arm 10 with the armature 5, the rocker arm 10 and the valve 12.
  • the spring 14 is supported on the stem of the valve 12 via a spring plate 17.
  • the movement of the armature 5 is delayed near the pole face of the magnet 2 by compressing air.
  • the cam ring 7 is provided with shoulders such that the outflow cross-section 58 between the armature 5 and the cam ring 7 is reduced before the armature 5 hits the pole face.
  • the rocker arm 10 is supported in the adjusting member 52 via a hydraulic length compensation element 51.
  • the acting force of the prestressed compression spring 14 is supported on the valve seat 16 via the spring plate 17, the stem of the valve 12 and the valve plate 15.
  • the armature 5 rests on the switching magnet 2, with a holding force that is greater than the force of the prestressed compression spring 13 minus the force of the spring 50.
  • the rocker arm 10 is force-free, so that the hydraulic compensating element 51 used compensate for the lengthening that occurs can and thus ensures that when the armature 5 rests on the pole face of the electromagnet 2, the valve plate 15 rests in the valve seat 16.
  • a soft magnetic bushing 55 supported in the adjusting member 52 on an inclined plane 54 changes the prestressing of the spring 50 when the adjusting member 52 is actuated and thus corrects the equilibrium position of the oscillating system. Furthermore, the soft magnetic sleeve 55 contains an annular recess 56 which, when the sleeve 55 moves, is displaced relative to a magnetically non-permeable ring 57 arranged in the magnet 1. Depending on the position of the soft magnetic sleeve 55, this results in a different magnetic resistance in the magnetic circuit of the magnet 1.
  • the adjusting member 52 is moved to the left. This shortens the lever arm l 1 and the lever arm l 2 is extended. This increases both the biasing force of the spring 14 acting on the armature 5 and the spring stiffness which is reduced on the armature side.
  • the biasing force of the spring 50 is reduced by the movement of the sleeve 55.
  • the increasing with increasing stroke holding forces on the opening magnet 1 are compensated for by reducing the magnetic resistance in the magnet 1, so that the required holding current and the fall time of the armature remain constant. This change is also caused by the movement of the sleeve 55.
  • the process is analogous when the stroke is reduced.
  • Figure 2 shows an electromagnetic actuator with a hydraulic transmission system consisting of the electromagnets 1 and 2, the armature 5, the valve 12 and the springs 13, 14 and 50.
  • the armature 5 displaces oil from a space 60 during its movement is located in cover 63 of the actuating device, through line 61 in cylinder 62.
  • cylinder 62 there is a three-part piston consisting of mushroom 64 and bushes 65 and 66. These have a bore 67 and 68 on the circumference, as well as cylinder 62 The bores of all three components are aligned when the valve 12 is in the closed position.
  • the adjusting member 69 has at its end a pin-shaped projection 70 which is guided in a bore 71 of the cylinder 62 and can engage in the bores 67 and 68 when the adjusting member 69 is displaced . This allows the sockets 65 and 66 to be locked.
  • the transmission ratio results from the ratio of the diameters of the acting cylinders d1 to d2, d3 and d4.
  • the adjusting member 69 has an inclined plane 73 which adjusts the prestress of the spring 50 via a bush 74 and a spring plate 75 and thus the equilibrium position of the oscillating one Systems tracks.
  • FIGS. 3 and 4 show an arrangement of 2 rocker arms 20 and 21 for actuating two valves or slides 22 and 23, respectively.
  • FIG. 5 shows an arrangement for actuating two valves or slides by means of a common rocker arm 26. This enables two or more valves or slides to be actuated with a small valve spacing.
  • Figure 6 shows a device for adjusting the equilibrium position of the vibrating system.
  • the position of the base point of the spring 13 is adjusted via two components 27 and 28 with wedge surfaces.
  • the component 27 is guided in a bore 29 of the housing 8.
  • Component 28 lies on the flat bottom 30 of the bore 29 and contains a radial threaded bore 31.
  • a bolt 32 is locked in the housing 8 by a stop 33 in its axial displacement and moves the component 28 in the direction of the longitudinal axis of the bolt when it rotates.
  • the device is self-locking.
  • FIG. 7 shows a device for adjusting the equilibrium position in accordance with the previously described type, but here a screw 34 with a wedge-shaped beveled surface 35 forms the counterpart to component 27.
  • the wedge surfaces lie only at a precisely defined position per revolution of the screw 34, so that the equilibrium position is set in discrete steps.
  • the device described is self-locking.
  • FIG. 8 shows a device for adjusting the equilibrium position, which is accessible in an axis parallel to the longitudinal axis 85 of the adjusting device.
  • a lever 36 rests on an abutment 37 and is positioned by an adjusting screw 38, which is supported in the housing 8.
  • the other end of the adjusting lever 36 acts on a spring support via a guided pin 39 40.
  • the device described is self-locking if the thread pitch of the screw 38 is chosen accordingly.
  • FIG. 9 shows a further possible arrangement of a hydraulic compensating element 76 between the housing 8 and the magnet 2 of an electromagnetic actuating device assigned to the closed position.
  • the axially displaceable assembly consisting of the magnets 1 and 2 and the lifting ring 7, can establish the frictional connection between the armature 5, rocker arm 10 and valve by the force of a compression spring acting in the compensating element 76.
  • FIGS. 10 and 11 show further possible arrangements of the compensating element on the rocker arm 10.
  • FIG. 12 shows a possible arrangement of the actuating unit 43, transmission element 10 and control element 12, the force being transmitted via a push rod 44.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Servomotors (AREA)
  • Switches With Compound Operations (AREA)
  • Massaging Devices (AREA)

Abstract

In order to adjust the stroke of a control element (15) which is actuated electromagnetically by a spring-mass oscillation system (5,13,50), for displacement machines and in order to permit a free arrangement of the electromagnetic positioning device in the housing (8), in particular in a cylinder head of a displacement machine, the movement of the positioning device is transmitted to the control element, in particular one or more stroke valves or flat slide valves by means of a mechanical or hydraulic transmission system (10) with a variable transmission ratio. In addition, devices (54,55) are described for exactly setting the position of equilibrium of the oscillating system. The electromagnetic positioning device can also be combined with a limit position damper (7) or with a hydraulic compensation element (51) of known design. <IMAGE>

Description

Die Erfindung bezieht sich auf eine elektromagnetisch arbeitende Stelleinrichtung für wenigstens ein oszillierend bewegbares Steuerelement für Verdrängungsmaschinen, insbesondere Flachschieber und Hubventile, mit zwei Schalt-Elektromagneten, welche der geöffneten und der geschlossenen Schaltposition wenigstens eines Steuerelements entsprechen, mit einem zwischen den beiden Schalt-Elektromagneten angeordneten, die Lage des Steuerelements bestimmenden Anker, und mit einem Federsystem zur oszillierenden Kraftübertragung auf den Anker zwischen den Schaltpositionen, welches so bemessen ist, daß der Ort der Gleichgewichtslage des Ankers zwischen den beiden Schaltpositionen liegt.The invention relates to an electromagnetically operating control device for at least one oscillatingly movable control element for displacement machines, in particular flat slide valves and globe valves, with two switching electromagnets, which correspond to the open and the closed switching position of at least one control element, with one arranged between the two switching electromagnets , The position of the control element determining armature, and with a spring system for oscillating force transmission to the armature between the switching positions, which is dimensioned such that the position of the equilibrium position of the armature lies between the two switching positions.

Eine derartige Stelleinrichtung ist aus DE-OS 30 24 109 bekannt. Das Steuerelement einer Verdrängungsmaschine wird bei einer Stelleinrichtung der aufgeführten Art durch eine Druckfeder in geschlossenem Zustand gehalten. Eine weitere Druckfeder wirkt auf einen mit dem Steuerelement zusammenwirkenden Magnetanker, so daß die Gleichgewichtslage des Federsystems in der Mitte oder nahe der Mitte zwischen den Endlagen der Bewegung des Magnetankers liegt. Die Endlagen der Ankerbewegung befinden sich jeweils an einem elektrisch betätigten Schaltmagnet. Zum Schalten dieser Vorrichtung wird jeweils ein Schaltmagnet erregt und der andere abgeschaltet. Aufgrund der Kraft der vorgespannten Feder wird der Anker bis zur Gleichgewichtslage beschleunigt und auf seinem weiteren Weg durch die dann bestimmende entgegenwirkende Kraft der anderen Feder verzögert. Aufgrund von Reibung kann der Anker die gegenüberliegende Endlage nicht erreichen. Auf dem fehlenden Restweg wird der Anker durch die Zugkraft des Schaltmagneten angezogen.Such an actuator is known from DE-OS 30 24 109. The control element of a displacement machine is held in the closed state by a compression spring in an actuating device of the type listed. Another compression spring acts on a magnet armature interacting with the control element, so that the equilibrium position of the spring system lies in the middle or near the middle between the end positions of the movement of the magnet armature. The end positions of the armature movement are each on an electrically operated switching magnet. To switch this device, one switching magnet is energized and the other switched off. Due to the force of the prestressed spring, the armature is accelerated to the equilibrium position and decelerated on its further path by the counteracting force of the other spring which then determines. Due to friction, the armature cannot reach the opposite end position. On the missing remaining path, the armature is attracted by the pulling force of the switching magnet.

Eine andere Ausführungsform einer derartigen elektromagnetisch arbeitenden Stelleinrichtung wird in EP-A-245 614 beschrieben.Another embodiment of such an electromagnetic actuator is described in EP-A-245 614.

Auch hierbei handelt es sich um ein schwingungsfähiges FederMasse-System mit einer Gleichgewichtslage zwischen zwei Schaltpositionen. Wesentliches Merkmal dieses Systems ist die Auslegung des Federsystems als Drehstabfeder mit einer Ventilbetätigung über einen mit der Drehstabfeder drehfest verbundenen Schlepphebel mit festem Übersetzungsverhältnis. Wesentliche Ziele sind dabei die Minimierung der bewegten Massen des Feder-Masse-Systems und die Vergrößerung des wirksamen Hubs des Tellerventils bei Hubbewegungen des Ankers für handelsübliche Elektromagnete.This is also an oscillating spring mass system with an equilibrium position between two switching positions. An essential feature of this system is the design of the spring system as a torsion bar spring with valve actuation via a rocker arm with a fixed transmission ratio that is connected to the torsion bar spring in a rotationally fixed manner. The main goals are to minimize the moving masses of the spring-mass system and to increase the effective stroke of the poppet valve when the armature moves for standard electromagnets.

Gegenüber Schaltsystemen, die den Anker über den gesamten Hub gegen die Kraft einer Feder anziehen, wird mit Systemen dieser Art eine Verringerung der Baugröße erzielt, da aufgrund des geringeren zu überbrückenden Luftspaltes die radiale Abmessung des Wicklungsfensters klein gehalten werden kann. Dies ist vor allem im Hinblick auf den Einsatz der Stelleinrichtung an Verdrängungsmaschinen von Bedeutung.Compared to switching systems that attract the armature over the entire stroke against the force of a spring, systems of this type achieve a reduction in size because the radial dimension of the winding window can be kept small due to the smaller air gap to be bridged. This is particularly important with regard to the use of the actuating device on displacement machines.

Der Arbeitshub einer solchen Stelleinrichtung ist so zu bemessen, daß für den größten auftretenden Massenstrom am Steuerelement einer Verdrängungsmaschine ein ausreichender Öffnungsquerschnitt zur Verfügung steht und damit eine Drosselung vermieden wird. Bei kleineren Massenströmen, die im Teillastbetrieb von Verdrängungsmaschinen und hier insbesondere von Brennkraftmaschinen auftreten, ist ein Betrieb der Stelleinrichtung bei diesem maximalen Arbeitshub jedoch unwirtschaftlich, da die zum Positionswechsel des Steuerelements zuzuführende elektrische Energie abhängig vom Hub des Steuerelements zunimmt. Weiterhin hat die Verringerung des Öffnungsquerschnitts eine Zunahme der Strömungsgeschwindigkeit am Steuerelement zur Folge, was zur Verbesserung der Aufbereitung von mehrphasigen Gemischen, insbesondere eines Luft-Kraftstoffgemisches bei Brennkraftmaschinen, beiträgt. Der ausführbare maximale Hub des Steuerventils wird jedoch bei den vorbekannten Bauarten durch die Abmessungen der Stelleinrichtung sowie durch die vorgegebene Positionierung in Verlängerung der Ventilachse begrenzt und ist nicht veränderbar.The working stroke of such an actuating device is to be dimensioned such that a sufficient opening cross-section is available for the largest mass flow occurring at the control element of a displacement machine and thus throttling is avoided. With smaller mass flows, which occur in partial load operation of displacement machines and here in particular internal combustion engines, operation of the actuating device at this maximum working stroke is uneconomical, since the electrical energy to be supplied for changing the position of the control element increases as a function of the stroke of the control element. Furthermore, the reduction in the opening cross-section results in an increase in the flow speed at the control element, which contributes to the improvement of the preparation of multiphase mixtures, in particular an air-fuel mixture in internal combustion engines. The executable maximum stroke of the control valve is, however, limited in the previously known types by the dimensions of the actuating device and by the predetermined positioning in the extension of the valve axis and cannot be changed.

In US-A-1 395 851 wird zwar eine Möglichkeit beschrieben, das Kipphebelübersetzungsverhältnis durch Verändern der Position der Kipphebelachse zu variieren, mit dem Ziel, durch einen der jeweiligen Motorleistung angepaßten Öffnungsquerschnitt eine Verbesserung des Wirkungsgrades zu erzielen. Mit dieser Vorrichtung lassen sich jedoch die Öffnungs- und Schließtzeiten der Ventile nur in direkter Abhängigkeit voneinander variieren. Insbesondere ist keine Veränderung der Ventilüberschneidung (Einlaß-Öffnet/Auslaß-Schließt) möglich, ohne gleichzeitig die übrigen Steuerzeiten Einlaß-Schließt und/oder Auslaß-Öffnet mit zu verändern. Dadurch ist die Variabilität dieses Systems stark eingeschränkt.US-A-1 395 851 describes a possibility of varying the rocker gear ratio by changing the position of the rocker arm axis, with the aim of achieving an improvement in efficiency by means of an opening cross section which is adapted to the respective engine power. With this device, however, the opening and closing times of the valves can only be varied in direct dependence on one another. In particular, it is not possible to change the valve overlap (inlet-opens / outlet-closes) without simultaneously changing the other control times inlet-closes and / or outlet-opens. This severely limits the variability of this system.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, bei möglichst kompakten Abmessungen der Stelleinrichtung und freierer Anordnung der Stelleinrichtung in der Aufnahme, insbesondere in einem Zylinderkopf für eine Brennkraftmaschine, eine flexible Anpassung der Stelleinrichtung an die jeweiligen Betriebsbedingungen und zugleich eine Energieersparnis zu erreichen.The object of the present invention is to achieve a flexible adaptation of the actuating device to the respective operating conditions and at the same time an energy saving with the most compact possible dimensions of the actuating device and a freer arrangement of the actuating device in the receptacle, in particular in a cylinder head for an internal combustion engine.

Diese Aufgabe wird erfindungsgemäß bei einer elektromagnetisch arbeitenden Stelleinrichtung der eingangs beschriebenen Art gelöst durch ein mit dem Anker und wenigstens einem Steuerelement zusammenwirkendes variables Kraftübertragungsystem, durch das der Anker das wenigstens eine Steuerelement über Mittel zur Änderung des Übertragungsverhältnisses hin- und herschaltet, wobei das Übertragungssystem so mit dem aus dem Federsystem, dem Anker um dem Steuerelement bestehenden schwingungsfähigen System verbunden ist, daß die Gleichgewichtslage des Ankers verstellbar ist, durch eine gemeinsame Vorrichtung zur gleichzeitigen Veränderung des Übersetzungsverhältnisses und des magnetischen Widerstandes im Magnetkreis eines oder beider Arbeitsmagnete zur Einstellung der Abfallzeiten des Ankers, und zur Anpassung der Gleichgewichtslage des schwingenden Systems an die neuen Federkräfte durch Änderung der Lage eines oder mehrerer Federfußpunkte.This object is achieved according to the invention in an electromagnetically operating control device of the type described in the introduction by means of a variable power transmission system which interacts with the armature and at least one control element, by means of which the armature switches the at least one control element back and forth via means for changing the transmission ratio, the transmission system thus is connected to the oscillating system consisting of the spring system, the armature around the control element, that the equilibrium position of the armature is adjustable, by a common device for simultaneously changing the transmission ratio and the magnetic resistance in the magnetic circuit of one or both working magnets for setting the fall times of the armature , and to adapt the equilibrium position of the vibrating system to the new spring forces by changing the position of one or more spring base points.

Um die Anordnung von Stelleinheit, Übertragungssystem und Steuerelement variabel zu gestalten, ist die Kraftübertragung durch Stößelstangen zweckmäßig.In order to make the arrangement of the actuating unit, transmission system and control element variable, the force transmission by push rods is expedient.

Gemäß einer weiteren Ausbildung der Erfindung ist das Übertragungssystem als im Übersetzungsverhältnis variables hydraulisches Getriebe ausgebildet.According to a further embodiment of the invention, the transmission system is designed as a hydraulic transmission which is variable in the transmission ratio.

Das schwingungsfähige Feder-Masse-System mit Druckfedern zu beiden Seiten des Ankers ist nach einer weiteren Ausführungsform der Erfindung so ausgebildet, daß die Federn oder Federpakete aufgeteilt sind in magnetseitig angeordnete Federn und steuerelementseitig angeordnete Federn.The vibratory spring-mass system with compression springs on both sides of the armature is designed according to a further embodiment of the invention so that the springs or spring assemblies are divided into springs arranged on the magnet side and springs arranged on the control element.

Nach einer weiteren Ausbildung der Erfindung ist vorgesehen, daß mehrere Steuerelemente mit je einem Übertragungssystem zusammenwirken, wobei bei Ventil-Verdrängungsmaschinen je ein Übertragungssystem pro Ventil oder ein gemeinsames Übertragungssystem für mehrere Ventile vorhanden ist.According to a further embodiment of the invention, it is provided that a plurality of control elements cooperate with one transmission system each, with valve displacement machines each having a transmission system per valve or a common transmission system for several valves.

Für die Einstellung der Gleichgewichtslage des schwingenden Systems ist nach einer weiteren Ausführungsform der Erfindung vorgesehen, den nichtbewegten Fußpunkt einer oder mehrerer Federn des schwingungsfähigen Systems verstellbar auszubilden. Dabei ist anzustreben, daß die Verstellung im Aufnahmegehäuse, insbesondere in dem Zylinderkopf einer Brennkraftmaschine, leicht zugänglich angeordnet ist, da die korrekte Einstellung der Gleichgewichtslage unter Betriebsbedingungen erfolgt. Diese Verstellung erfolgt nach weiteren Ausbildungen der Erfindung entweder direkt über eine Verschiebung von Keilflächen zueinander oder über ein Übertragungsglied, welches als Kipp- oder Schlepphebel ausgebildet ist.In order to set the equilibrium position of the vibrating system, a further embodiment of the invention provides for the non-moving base point of one or more springs of the vibratable system to be adjustable. The aim here is that the adjustment in the receiving housing, in particular in the cylinder head of an internal combustion engine, is arranged so that it is easily accessible, since the correct setting of the equilibrium position takes place under operating conditions. According to further developments of the invention, this adjustment takes place either directly by shifting wedge surfaces relative to one another or via a transmission member which is designed as a rocker arm or finger follower.

Zur spielfreien Betätigung der oszillierend bewegten Bauteile ist gemäß einer weiteren Ausbildung der Erfindung ein hydraulisches Ausgleichselement vorgesehen. Das Ausgleichselement kann erfindungsgemäß an verschiedenen Positionen innerhalb der bewegten Bauteile angeordnet sein, insbesondere im Übertragungssystem oder im Magnetanker.According to a further embodiment of the invention, a hydraulic compensation element is provided for the play-free actuation of the oscillating components. According to the invention, the compensating element can be arranged at different positions within the moving components, in particular in the transmission system or in the magnet armature.

Gemäß einer weiteren Ausbildung der Erfindung ist das hydraulische Ausgleichselement zwischen dem Aufnahmegehäuse und dem der geschlossenen Ventilposition zugeordneten Schaltmagneten angeordnet, wobei die axiale Verschiebung des Schaltmagneten die in den bewegten Bauteilen entstehenden Längenänderungen ausgleicht.According to a further embodiment of the invention, the hydraulic compensating element is arranged between the receptacle housing and the switching magnet assigned to the closed valve position, the axial displacement of the switching magnet compensating for the changes in length that occur in the moving components.

Eine weitere vorteilhafte Ausbildung der Erfindung besteht in der Anordnung des hydraulischen Ausgleichselementes zwischen der Lagerung des Übertragungsgliedes und dem Aufnahmegehäuse bzw. dem Verstellglied.A further advantageous embodiment of the invention consists in the arrangement of the hydraulic compensating element between the mounting of the transmission element and the receiving housing or the adjusting element.

Eine weitere vorteilhafte Ausbildung der Erfindung besteht in dem Einsatz von Permanentmagneten in den Schaltmagneten.Another advantageous embodiment of the invention consists in the use of permanent magnets in the switching magnets.

Eine andere Ausbildung der Erfindung bezieht sich auf eine Dämpfung der Ankerbewegung kurz vor dem Erreichen der Endlagen.Another embodiment of the invention relates to damping the armature movement shortly before reaching the end positions.

Um die Gleichgewichtslage des schwingenden Systems bei der Veränderung des Übersetzungsverhältnisses nachzuführen, kann gemäß weiterer Ausbildungen der Erfindung der Fußpunkt einer der dem schwingungsfähigen System zugeordneten Federn oder Federpakete verstellt werden.In order to track the equilibrium position of the oscillating system when the transmission ratio changes, the base point of one of the springs or spring assemblies assigned to the oscillatory system can be adjusted according to further developments of the invention.

Gemäß einer weiteren Ausbildung der Erfindung wird der magnetische Widerstand des Magnetkreises eines oder beider Arbeitsmagnete beim Wechsel der Übersetzung des Übertragungssystems und damit bei Änderung der wirksamen Federkräfte verändert, mit dem Ziel, die Zeitspanne zwischen dem Abschalten des Stromes eines Arbeitsmagneten und dem Beginn der Ankerbewegung, im folgenden Abfallzeit genannt, konstant zu halten.According to a further embodiment of the invention, the magnetic resistance of the magnetic circuit of one or both working magnets is changed when the ratio of the transmission system changes and thus when the effective spring forces change, with the aim of changing the time between the switching off of the current Keep working magnets and the beginning of the armature movement, hereinafter called fall time, constant.

Gemäß einer weiteren vorteilhaften Ausbildung der Erfindung erfolgt sowohl die Veränderung des magnetischen Widerstandes als auch die Verstellung der Übersetzung des Übertragungsgliedes und der Gleichgewichtslage des schwingenden Systems durch eine gemeinsame Vorrichtung.According to a further advantageous embodiment of the invention, both the change in the magnetic resistance and the adjustment of the translation of the transmission element and the equilibrium position of the vibrating system are carried out by a common device.

Durch die Erfindung wird in vorteilhafter Weise eine Veränderung des Schalthubes der Stelleinrichtung und damit des wirksamen Öffnungsquerschnittes des Hubventils oder Flachschiebers bei weitgehender Beibehaltung der kompakten Abmessungen der Stelleinrichtung erreicht. Weiterhin ist im Vergleich zu der Anordnung einer Stelleinrichtung in direkter Verlängerung des Schaftes des Steuerelements eine Vergrößerung des maximalen Hubes des Steuerelementes möglich. Ein weiterer Vorteil besteht darin, daß die Stelleinrichtung innerhalb eines durch das Übertragungssystem vorgegebenen Radius um den Ventilschaft angeordnet werden kann und damit eine größere Gestaltungsfreiheit des Aufnahmegehäuses erzielt wird. Auch wird durch die Erfindung eine exakte Justierung der Gleichgewichtslage des schwingenden Systems im eingebauten Zustand ermöglicht, sowie die Nachführung der Gleichgewichtslage des schwingenden Systems bei Veränderung des Übersetzungsverhältnisses des Übertragungssystems. Durch die Veränderung des magnetischen Widerstandes des Magnetkreises ist die Einstellung konstanter Abfallzeiten des Ankers bei unterschiedlichen Übersetzungsverhältnissen des Übertragungssystems möglich. Weiterhin ist in vorteilhafter Weise eine Kompensation der im Betrieb aufgrund von Wärmedehnung und Verschleiß auftretenden Längenänderungen der bewegten Bauteile durch ein hydraulisches Ausgleichselement möglich, dessen Position in der Stellvorrichtung so gewählt werden kann, daß ein negativer Einfluß auf die von Masse und Federsteifigkeit bestimmte Schaltzeit der Stellvorrichtung vermieden wird.The invention advantageously changes the switching stroke of the adjusting device and thus the effective opening cross-section of the lifting valve or flat slide valve while largely maintaining the compact dimensions of the adjusting device. Furthermore, compared to the arrangement of an actuating device in a direct extension of the shaft of the control element, an increase in the maximum stroke of the control element is possible. A further advantage is that the actuating device can be arranged around the valve stem within a radius predetermined by the transmission system, and thus greater freedom of design for the receiving housing is achieved. The invention also enables an exact adjustment of the equilibrium position of the vibrating system in the installed state, and the tracking of the equilibrium position of the vibrating system when the transmission ratio of the transmission system changes. By changing the magnetic resistance of the magnetic circuit, it is possible to set constant fall times of the armature with different transmission ratios of the transmission system. Furthermore, a compensation of the changes in length of the moving components occurring during operation due to thermal expansion and wear is advantageously possible by means of a hydraulic compensating element, the position of which in the adjusting device can be selected such that a negative influence on the Mass and spring stiffness certain switching time of the actuator is avoided.

Ausführungsbeispiele der Erfindung werden nachfolgend anhand der Zeichnungen beschrieben.

  • Fig. 1 zeigt im Längsschnitt ein Ausführungsbeispiel der Vorrichrichtung gemäß der Erfindung mit einem Kipphebel als Übertragungssystem sowie einer Verstellung der Gleichgewichtslage des schwingenden Systems durch Verlagerung eines Federfußpunktes und der Veränderung des magnetischen Widerstandes des Öffnet-Magneten. Weiterhin ist ein hydraulisches Ventilspielausgleichselement sowie eine Endlagendämpfung des Ankers dargestellt.
  • Fig. 2 zeigt im Längsschnitt ein Ausführungsbeispiel der Vorrichrichtung mit einem hydraulischen Übertragungssystem.
  • Fig. 3, 4 und 5 zeigen in Seitenansicht bzw. Aufsicht Ausführungsbeispiele mit zwei betätigten Ventilen pro Stelleinrichtung gemäß der Erfindung.
  • Fig. 6, 7 und 8 zeigen im Schnitt bevorzugte Ausbildungen von Vorrichtungen zur Einstellung der Gleichgewichtslage des schwingenden Systems gemäß der Erfindung.
  • Fig. 9, 10 und 11 zeigen weitere vorteilhafte Anordnungen des hydraulischen Ausgleichselementes gemäß der Erfindung.
  • Fig. 12 zeigt eine Anordnung von Stelleinrichtung, Übertragungsglied und Steuerelement bei der die Kraftübertragung mit Hilfe einer Stößelstange erfolgt.
Embodiments of the invention are described below with reference to the drawings.
  • Fig. 1 shows in longitudinal section an embodiment of the device according to the invention with a rocker arm as a transmission system and an adjustment of the equilibrium position of the vibrating system by shifting a spring base and changing the magnetic resistance of the opening magnet. Furthermore, a hydraulic valve lash adjuster and end position damping of the armature are shown.
  • Fig. 2 shows in longitudinal section an embodiment of the device with a hydraulic transmission system.
  • 3, 4 and 5 show, in side view and top view, exemplary embodiments with two actuated valves per actuating device according to the invention.
  • 6, 7 and 8 show in section preferred configurations of devices for adjusting the equilibrium position of the vibrating system according to the invention.
  • 9, 10 and 11 show further advantageous arrangements of the hydraulic compensation element according to the invention.
  • Fig. 12 shows an arrangement of actuating device, transmission member and control element in which the power transmission takes place with the aid of a push rod.

Figur 1 zeigt beispielhaft eine elektromagnetisch arbeitende Stelleinrichtung mit Elektromagneten 1 und 2, Wicklungen 3 und 4 sowie Anker 5. Die Elektromagneten 1 und 2 sind durch einen Deckel 6 sowie unter Zwischenschaltung eines Hubringes 7 fest in Gehäuse 8 eingespannt. Der Anker 5 ist in einer Hülse 53 geführt und betätigt über einen Kipphebel 10 ein Ventil 12. Druckfedern 13, 14 und 50 bilden unter Berücksichtigung des Übersetzungsverhältnisses des Kipphebels 10 mit dem Anker 5, dem Kipphebel 10 und dem Ventil 12 das schwingende System. Die Feder 14 ist über einen Federteller 17 am Schaft des Ventils 12 abgestützt. Die Bewegung des Ankers 5 wird nahe der Polfläche des Magneten 2 durch Verdichten von Luft verzögert. Zu diesem Zweck ist der Hubring 7 derart mit Absätzen versehen, daß vor dem Auftreffen des Ankers 5 auf der Polfläche der Abströmquerschnitt 58 zwischen dem Anker 5 und dem Hubring 7 verringert wird.FIG. 1 shows an example of an electromagnetically operating actuating device with electromagnets 1 and 2, windings 3 and 4 and armature 5. The electromagnets 1 and 2 are fixed in by a cover 6 and with the interposition of a cam ring 7 Housing 8 clamped. The armature 5 is guided in a sleeve 53 and actuates a valve 12 via a rocker arm 10. Pressure springs 13, 14 and 50 form the oscillating system, taking into account the transmission ratio of the rocker arm 10 with the armature 5, the rocker arm 10 and the valve 12. The spring 14 is supported on the stem of the valve 12 via a spring plate 17. The movement of the armature 5 is delayed near the pole face of the magnet 2 by compressing air. For this purpose, the cam ring 7 is provided with shoulders such that the outflow cross-section 58 between the armature 5 and the cam ring 7 is reduced before the armature 5 hits the pole face.

Der Kipphebel 10 ist über ein hydraulisches Längenausgleichselement 51 in Verstellglied 52 abgestützt. Bei geschlossenem Ventil 12 stützt sich die wirkende Kraft der vorgespannten Druckfeder 14 über den Federteller 17, den Schaft des Ventils 12 und den Ventilteller 15 am Ventilsitz 16 ab. Der Anker 5 liegt am Schaltmagneten 2 an, und zwar mit einer Haltekraft, die größer ist als die Kraft der vorgespannten Druckfeder 13 abzüglich der Kraft der Feder 50. Damit ist der Kipphebel 10 kraftfrei, so daß das eingesetzte hydraulische Ausgleichselement 51 die auftretende Längenängerung kompensieren kann und damit sicherstellt, daß bei Auflage des Ankers 5 an der Polfläche des Elektromagneten 2 der Ventilteller 15 im Ventilsitz 16 anliegt.The rocker arm 10 is supported in the adjusting member 52 via a hydraulic length compensation element 51. When the valve 12 is closed, the acting force of the prestressed compression spring 14 is supported on the valve seat 16 via the spring plate 17, the stem of the valve 12 and the valve plate 15. The armature 5 rests on the switching magnet 2, with a holding force that is greater than the force of the prestressed compression spring 13 minus the force of the spring 50. Thus, the rocker arm 10 is force-free, so that the hydraulic compensating element 51 used compensate for the lengthening that occurs can and thus ensures that when the armature 5 rests on the pole face of the electromagnet 2, the valve plate 15 rests in the valve seat 16.

Eine im Verstellglied 52 an einer schiefen Ebene 54 abgestützte weichmagnetische Büchse 55 verändert bei Betätigung des Verstellgliedes 52 die Vorspannung der Feder 50 und korrigiert so die Gleichgewichtslage des schwingenden Systems. Weiterhin enthält die weichmagnetische Büchse 55 eine ringförmige Aussparung 56, die bei Bewegung der Büchse 55 relativ zu einem im Magneten 1 angeordneten, magnetisch nichtpermeablen Ring 57 verschoben wird. Je nach Position der weichmagnetischen Büchse 55 ergibt sich so ein unterschiedlicher magnetischer Widerstand im Magnetkreis des Magneten 1.A soft magnetic bushing 55 supported in the adjusting member 52 on an inclined plane 54 changes the prestressing of the spring 50 when the adjusting member 52 is actuated and thus corrects the equilibrium position of the oscillating system. Furthermore, the soft magnetic sleeve 55 contains an annular recess 56 which, when the sleeve 55 moves, is displaced relative to a magnetically non-permeable ring 57 arranged in the magnet 1. Depending on the position of the soft magnetic sleeve 55, this results in a different magnetic resistance in the magnetic circuit of the magnet 1.

Zur Vergrößerung des Hubes des Ventils 12 wird das Verstellglied 52 nach links bewegt. Damit verkürzt sich der Hebelarm l₁, und der Hebelarm l₂ wird verlängert. Dadurch vergrößern sich sowohl die am Anker 5 wirkende Vorspannkraft der Feder 14 als auch deren auf die Ankerseite reduzierte Federsteifigkeit. Um die daraus folgende Verschiebung der Gleichgewichtslage des schwingenden Systems zu kompensieren, wird die Vorspannkraft der Feder 50 durch die Bewegung der Büchse 55 verringert. Die bei steigendem Hub zunehmenden Haltekräfte am Öffnet-Magneten 1 werden durch Verringerung des magnetischen Widerstandes im Magneten 1 ausgeglichen, so daß der benötigte Haltestrom sowie die Abfallzeit des Ankers konstant bleiben. Diese Veränderung wird ebenfalls durch die Bewegung der Büchse 55 bewirkt. Der Vorgang erfolgt bei Verkleinerung des Hubes sinngemäß.To increase the stroke of the valve 12, the adjusting member 52 is moved to the left. This shortens the lever arm l 1 and the lever arm l 2 is extended. This increases both the biasing force of the spring 14 acting on the armature 5 and the spring stiffness which is reduced on the armature side. In order to compensate for the resulting shift in the equilibrium position of the oscillating system, the biasing force of the spring 50 is reduced by the movement of the sleeve 55. The increasing with increasing stroke holding forces on the opening magnet 1 are compensated for by reducing the magnetic resistance in the magnet 1, so that the required holding current and the fall time of the armature remain constant. This change is also caused by the movement of the sleeve 55. The process is analogous when the stroke is reduced.

Figur 2 zeigt eine elektromagnetisch arbeitende Stelleinrichtung mit einem hydraulischen Übertragungssystem, bestehend aus den Elektromagneten 1 und 2, dem Anker 5, dem Ventil 12 und den Federn 13, 14 und 50. Der Anker 5 verdrängt bei seiner Bewegung Öl aus einem Raum 60, der sich in Deckel 63 der Stelleinrichtung befindet, durch Leitung 61 in Zylinder 62. Im Zylinder 62 ist ein dreigeteilter Kolben vorhanden, bestehend aus Pilz 64 und Buchsen 65 und 66. Diese haben am Umfang je eine Bohrung 67 bzw. 68, ebenso der Zylinder 62. Die Bohrungen aller drei Bauteile fluchten bei geschlossener Position des Ventils 12. Verstellglied 69 verfügt an seinem Ende über einen stiftförmigen Ansatz 70, der in einer Bohrung 71 des Zylinders 62 geführt ist und bei Verschiebung des Verstellgliedes 69 in die Bohrungen 67 und 68 greifen kann. Damit können die Buchsen 65 bzw. 66 arretiert werden. Das Übersetzungsverhältnis ergibt sich aus dem Verhältnis der Durchmesser der wirkenden Zylinder d1 zu d2, d3 bzw. d4. Weiterhin verfügt das Verstellglied 69 über eine schiefe Ebene 73, die über eine Büchse 74 und einen Federteller 75 die Vorspannung der Feder 50 verstellt und so die Gleichgewichtslage des schwingenden Systems nachführt.Figure 2 shows an electromagnetic actuator with a hydraulic transmission system consisting of the electromagnets 1 and 2, the armature 5, the valve 12 and the springs 13, 14 and 50. The armature 5 displaces oil from a space 60 during its movement is located in cover 63 of the actuating device, through line 61 in cylinder 62. In cylinder 62 there is a three-part piston consisting of mushroom 64 and bushes 65 and 66. These have a bore 67 and 68 on the circumference, as well as cylinder 62 The bores of all three components are aligned when the valve 12 is in the closed position. The adjusting member 69 has at its end a pin-shaped projection 70 which is guided in a bore 71 of the cylinder 62 and can engage in the bores 67 and 68 when the adjusting member 69 is displaced . This allows the sockets 65 and 66 to be locked. The transmission ratio results from the ratio of the diameters of the acting cylinders d1 to d2, d3 and d4. Furthermore, the adjusting member 69 has an inclined plane 73 which adjusts the prestress of the spring 50 via a bush 74 and a spring plate 75 and thus the equilibrium position of the oscillating one Systems tracks.

Figuren 3 und 4 zeigen eine Anordnung von 2 Kipphebeln 20 und 21 zur Betätigung zweier Ventile oder Schieber 22 bzw. 23.FIGS. 3 and 4 show an arrangement of 2 rocker arms 20 and 21 for actuating two valves or slides 22 and 23, respectively.

Figur 5 zeigt eine Anordnung zur Betätigung zweier Ventile oder Schieber mittels eines gemeinsamen Kipphebels 26. Damit ist eine Betätigung zweier oder auch mehrerer Ventile oder Schieber mit einem geringen Ventilabstand möglich.FIG. 5 shows an arrangement for actuating two valves or slides by means of a common rocker arm 26. This enables two or more valves or slides to be actuated with a small valve spacing.

Figur 6 zeigt eine Vorrichtung zur Einstellung der Gleichgewichtslage des schwingenden Systems. Dabei wird die Lage des Fußpunktes der Feder 13 über zwei Bauteile 27 und 28 mit Keilflächen verstellt. Das Bauteil 27 ist in einer Bohrung 29 des Gehäuses 8 geführt. Bauteil 28 liegt auf dem ebenen Boden 30 der Bohrung 29 auf und enthält eine radiale Gewindebohrung 31. Ein Bolzen 32 ist im Gehäuse 8 durch einen Anschlag 33 in seiner axialen Verschiebung arretiert und bewegt bei Drehung das Bauteil 28 in Richtung der Bolzenlängsachse. Die Vorrichtung ist selbsthemmend.Figure 6 shows a device for adjusting the equilibrium position of the vibrating system. The position of the base point of the spring 13 is adjusted via two components 27 and 28 with wedge surfaces. The component 27 is guided in a bore 29 of the housing 8. Component 28 lies on the flat bottom 30 of the bore 29 and contains a radial threaded bore 31. A bolt 32 is locked in the housing 8 by a stop 33 in its axial displacement and moves the component 28 in the direction of the longitudinal axis of the bolt when it rotates. The device is self-locking.

Figur 7 zeigt eine Vorrichtung zur Einstellung der Gleichgewichtslage entsprechend der vorher beschriebenen Art, wobei hier jedoch eine Schraube 34 mit keilförmig angeschrägter Fläche 35 das Gegenstück zu Bauteil 27 bildet. Bei dieser Ausführung liegen sich die Keilflächen jedoch nur an einer genau definierten Position pro Umdrehung der Schraube 34 gegenüber, so daß eine Einstellung der Gleichgewichtslage in diskreten Schritten erfolgt. Die beschriebene Vorrichtung ist selbsthemmend.FIG. 7 shows a device for adjusting the equilibrium position in accordance with the previously described type, but here a screw 34 with a wedge-shaped beveled surface 35 forms the counterpart to component 27. In this embodiment, however, the wedge surfaces lie only at a precisely defined position per revolution of the screw 34, so that the equilibrium position is set in discrete steps. The device described is self-locking.

Figur 8 zeigt eine Vorrichtung zur Verstellung der Gleichgewichtslage, die in einer Achse parallel zur Längsachse 85 der Stelleinrichtung zugänglich ist. Ein Hebel 36 liegt auf einem Widerlager 37 auf und wird durch eine Einstellschraube 38, die sich im Gehäuse 8 abstützt, positioniert. Das andere Ende des Einstellhebels 36 wirkt über einen geführten Stift 39 auf Federunterlage 40. Die beschriebene Vorrichtung ist bei entsprechender Wahl der Gewindesteigung der Schraube 38 selbsthemmend.FIG. 8 shows a device for adjusting the equilibrium position, which is accessible in an axis parallel to the longitudinal axis 85 of the adjusting device. A lever 36 rests on an abutment 37 and is positioned by an adjusting screw 38, which is supported in the housing 8. The other end of the adjusting lever 36 acts on a spring support via a guided pin 39 40. The device described is self-locking if the thread pitch of the screw 38 is chosen accordingly.

Figur 9 zeigt eine weitere mögliche Anordnung eines hydraulischen Ausgleichselementes 76 zwischen dem Gehäuse 8 und dem der Schließt-Position zugeordneten Magneten 2 einer elektromagnetischen Stelleinrichtung. Bei Anliegen des Ankers 5 am Magneten 2 kann die axial verschiebbare Baugruppe, bestehend aus den Magneten 1 und 2 sowie dem Hubring 7, durch die Kraft einer im Ausgleichselement 76 wirkenden Druckfeder den Kraftschluß zwischen Anker 5, Kipphebel 10 und Ventil herstellen.FIG. 9 shows a further possible arrangement of a hydraulic compensating element 76 between the housing 8 and the magnet 2 of an electromagnetic actuating device assigned to the closed position. When the armature 5 bears against the magnet 2, the axially displaceable assembly, consisting of the magnets 1 and 2 and the lifting ring 7, can establish the frictional connection between the armature 5, rocker arm 10 and valve by the force of a compression spring acting in the compensating element 76.

In Figur 10 und 11 sind weitere mögliche Anordnungen des Ausgleichselementes am Kipphebel 10 dargestellt.FIGS. 10 and 11 show further possible arrangements of the compensating element on the rocker arm 10.

Figur 12 zeigt eine mögliche Anordnung von Stelleinheit 43, Übertragungsglied 10 und Steuerelement 12, wobei die Kraftübertragung über eine Stößelstange 44 geschieht.FIG. 12 shows a possible arrangement of the actuating unit 43, transmission element 10 and control element 12, the force being transmitted via a push rod 44.

Claims (17)

  1. An electromagnetic positioning device for at least one control element (12), movable in oscillation, for displacement machines, especially flat slide valves and gate valves, comprising two switching electromagnets (1, 2) corresponding to the opened and closed switching positions of at least one control element (12), an armature (5) disposed between the two switching electromagnets (1, 2) and determining the position of the control element (12), and a spring system (13, 14, 50) for transmitting oscillating force to the armature (5) between the switching positions and dimensioned so that the equilibrium position of the armature (5) lies between the two switching positions, characterised by a variable force transmission system (10, 52) which co-operates with the armature (5) and with the at least one control element (12), enabling the armature (5) to move the at least one control element (12) in reciprocation via means (52, 54, 69, 73) for altering the transmission ratio, the transmission system being connected to the oscillating system comprising the spring system (13, 14, 50), the armature (5) and the control element (12) so that the equilibrium position of the armature (5) is adjustable by a common device (52) for simultaneously varying the transmission ratio and the reluctance (55, 56, 57) in the magnetic circuit of one or more working magnets (1, 2) for adjusting the drop-out times of the armature (5) and for adjusting the equilibrium position of the oscillating system to the new spring forces by altering the position of one or more spring feet.
  2. A positioning device according to claim 1, characterised in that the transmission system is a mechanical gear unit (10, 51, 52).
  3. A positioning device according to claim 1 or 2, characterised in that the transmission system contains a mechanical component, preferably a push rod (44), for transmitting compressive forces.
  4. A positioning device according to claim 1, characterised in that the transmission system is a hydraulic gear unit (60 - 71).
  5. A positioning device according to any of claims 1 to 4, characterised in that, on both sides of the transmission system, the spring system is divided into a number of springs (13, 50 and 14).
  6. A positioning device according to claim 5, characterised in that the springs (13, 50 and 14) disposed on each side of the transmission system comprise a number of individual springs varying in stiffness.
  7. A positioning device according to any of claims 1 to 6, characterised in that each transmission system (26) co-operates with a number of control elements.
  8. A positioning device according to claim 1, characterised in that the equilibrium position is adjustable via two wedge surfaces (27, 28) movable relatively to one another.
  9. A positioning device according to claim 8, characterised in that the wedge surfaces (27, 28) are movable relatively to one another via a screw thread (32).
  10. A positioning device according to claim 8 or 9, characterised in that one of the wedge surfaces (35) is permanently connected to the movable part of the thread (34).
  11. A positioning device according to claim 1, characterised in that the equilibrium position is adjustable via a transmission element in the form of a rocker arm or drag lever (36).
  12. A positioning device according to any of claims 1 to 7, characterised by at least one valve clearance-compensating element (51) for compensating the clearance caused by, or occurring at, the transmission system.
  13. A positioning device according to claim 12, characterised in that the valve clearance-compensating element (51, 76) is disposed in the transmission system either on the side of the control element or on the magnet side.
  14. A positioning device according to claim 12, characterised in that the valve clearance-compensating element (76) is disposed between the bearing of the transmission system and the stationary casing (8).
  15. A positioning device according to claim 12, characterised in that the valve clearance-adjusting element (76) is disposed between the closed-position magnet (2) and the casing (8).
  16. A positioning device according to any of claims 1 to 15, characterised in that permanent magnets are disposed in one or both switching magnets (1, 2).
  17. A positioning device according to any of claims 1 to 16, characterised in that the motion of the switching system is damped (58) near the end positions in one or both directions of motion.
EP90110559A 1989-06-27 1990-06-05 Electromagnetic positioning device Expired - Lifetime EP0405187B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90110559T ATE95277T1 (en) 1989-06-27 1990-06-05 ELECTROMAGNETIC ACTUATOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3920931A DE3920931A1 (en) 1989-06-27 1989-06-27 ELECTROMAGNETIC OPERATING DEVICE
DE3920931 1989-06-27

Publications (2)

Publication Number Publication Date
EP0405187A1 EP0405187A1 (en) 1991-01-02
EP0405187B1 true EP0405187B1 (en) 1993-09-29

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Family Applications (1)

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EP90110559A Expired - Lifetime EP0405187B1 (en) 1989-06-27 1990-06-05 Electromagnetic positioning device

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US (1) US5117213A (en)
EP (1) EP0405187B1 (en)
AT (1) ATE95277T1 (en)
DE (2) DE3920931A1 (en)

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Also Published As

Publication number Publication date
DE3920931A1 (en) 1991-01-03
EP0405187A1 (en) 1991-01-02
ATE95277T1 (en) 1993-10-15
US5117213A (en) 1992-05-26
DE59002881D1 (en) 1993-11-04

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