EP0244878B1 - Electromagnetic-hydraulic valve drive for an internal-combustion engine - Google Patents

Electromagnetic-hydraulic valve drive for an internal-combustion engine Download PDF

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Publication number
EP0244878B1
EP0244878B1 EP87107613A EP87107613A EP0244878B1 EP 0244878 B1 EP0244878 B1 EP 0244878B1 EP 87107613 A EP87107613 A EP 87107613A EP 87107613 A EP87107613 A EP 87107613A EP 0244878 B1 EP0244878 B1 EP 0244878B1
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EP
European Patent Office
Prior art keywords
piston
electromagnet
valve drive
armature
valve
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
EP87107613A
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German (de)
French (fr)
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EP0244878A2 (en
EP0244878A3 (en
Inventor
Gabriel Dipl.-Ing. Tittizer
Ewald Dipl.-Ing. Junghans
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Interatom Internationale Atomreaktorbau GmbH
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Interatom Internationale Atomreaktorbau GmbH
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Priority claimed from DE19853504639 external-priority patent/DE3504639A1/en
Application filed by Interatom Internationale Atomreaktorbau GmbH filed Critical Interatom Internationale Atomreaktorbau GmbH
Priority to AT87107613T priority Critical patent/ATE57989T1/en
Publication of EP0244878A2 publication Critical patent/EP0244878A2/en
Publication of EP0244878A3 publication Critical patent/EP0244878A3/en
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Publication of EP0244878B1 publication Critical patent/EP0244878B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/02—Systems with continuously-operating input and output apparatus
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder

Definitions

  • the present application relates to the electromagnetic valve train of an internal combustion engine, i.e. for four-stroke gasoline or diesel engines, with a first electromagnet that can be excited as a function of the operating parameters, in particular synchronously with the engine speed, and an armature that can be attracted by the first electromagnet.
  • Such machines have at least 2 valves per cylinder, which according to the currently preferred technique are pressed into their closed position by spring force and thereby brought into their open position in that a force which counteracts and exceeds the spring force is applied to the valve stem; this in such a way that cams are mounted on an auxiliary shaft driven by the crankshaft at half the speed, which apply the required force to the valve tappets via rocker arms.
  • cams and rocker arms are exposed to considerable wear due to sliding against one another, and the valve lift that can be achieved is limited in that the flank pitch of the cams cannot be chosen to be as large as desired if the forces to be exerted when they interact with the rocker arms should not exceed the permissible level.
  • Electromagnetic valve trains are already known, namely from DE-A 3 311 250 and EP-A 0 043 426.
  • an attempt is made to close the valve, which is designed as an armature of an electromagnet, via the selected displacement path (for example in a motor vehicle engine of 100 KW can be a few mm) by exciting the former.
  • This requires relatively large electromagnets, which are not only complex, but also often difficult to accommodate in the immediate vicinity of the engine block.
  • FR-A 932 936 devices for actuating valves are known in which a first piston slides on the conventional cam of a camshaft instead of the rocker arm; this displaces hydraulic fluid from its cylinder or takes it up again when moving backward. The hydraulic fluid in turn moves a second piston, which actuates the valve itself. From this document, the person skilled in the art can further see that the hydraulic transmission can also have a step-up or step-down if the cross sections of the two pistons are selected differently. However, there is no reason to use this option from the scriptures.
  • the object of the present invention is to enable a greater valve lift while basically adhering to the traditional design of the aforementioned motors and at the same time to eliminate parts which are susceptible to wear. This is intended to achieve a more favorable control behavior of the valves.
  • the solution to this problem is characterized in that the displacement of the armature is approximately 1-1.5 mm; by a first piston which slides in a first hydraulic cylinder and is connected to the armature, a second piston which acts on the valve stem and has a reduced diameter compared to the first piston and which slides in a second hydraulic cylinder, and a line connecting the first and second hydraulic cylinders .
  • the hydraulic power transmission 1 can translate the movement of the first piston in that the second piston has a noticeably smaller cross section than the first piston.
  • the former then follows the movement imposed by the latter with a stroke which is enlarged in relation to the cross-sectional areas when the overall system is closed.
  • the movement of the pistons in their cylinders is largely wear-free due to the lack of transverse forces that stress the sliding surfaces. Since the armature of the proposed first electromagnet only needs to be communicated a very small displacement in the order of magnitude of 1 to 1.5 mm, relatively low electromagnetic forces are sufficient. This slight movement is then increased by the hydraulic ratio to the desired valve lift.
  • the return of the armature to its initial position when the electromagnet is de-energized can be effected in a conventional manner by the force of a return spring.
  • this return spring can be dispensed with in an embodiment of the invention according to claim 2, or its strength can be reduced to the extent which is sufficient to compensate for mechanical play if a special electromagnet is present for each movement device of the primary piston, which is mutually excited with the other.
  • the differential piston arrangement has the effect that a displacement of one piston, no matter in which direction, always results in a corresponding displacement of the other piston.
  • a pot magnet appears to be particularly suitable for use in the construction described, as proposed in claim 3.
  • the second piston and the valve stem with the integrally formed valve plate can be made in one piece, which also further reduces the possibility of play in the transmission.
  • FIG. 1 An embodiment of the invention is shown in the drawing, namely in the longitudinal axial section.
  • the figure partially shows the combustion chamber 1 of a cylinder of an internal combustion engine machine to which a fuel / air mixture is supplied via an intake duct 2; an outlet valve can be designed in basically the same way.
  • the intake duct 2 is closed off from the combustion chamber 1 by a valve disk 4, which forms a unit with a tappet 5.
  • the valve 4 is loaded in the direction of its closed position by a helical spring 6, which is supported on an abutment 7.
  • the first piston 12 is made in one piece with an armature 19.
  • the armature 19 is in contact with a first electromagnet 20 or a second electromagnet 21, depending on the alternating excitation to be carried out.
  • the air gap s to the electromagnet removed in each case is only about 1 to 1.5 mm in size, so that relatively weak and thus small electromagnets can be used. This is particularly the case when, as shown here, it is not necessary to work against a strong return spring, but rather a spring 6, which presses the valve plate 4 into its closed position, only serves to compensate for play and can be dimensioned correspondingly weak.
  • the excitation of the electromagnets 20, 21 takes place alternately by a control unit 26, in which not only the respective, for. B. on a crankshaft 27 decreased speed of the machine, but also other operating values that are detected by sensors 28 not described here. In this way, the valve closing times that correspond most precisely to the respective operating state can be controlled.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Die vorliegende Anmeldung betrifft den elektromagnetischen Ventiltrieb einer Verbrennungskraftmaschine, d.h. für Viertakt-Otto- bzw. Dieselmotoren, mit einem in Abhängigkeit von den Betriebsparametern, insbesondere synchron zur Motordrehzahl, erregbaren ersten Elektromagneten und einem durch den ersten Elektromagneten anziehbaren Anker.The present application relates to the electromagnetic valve train of an internal combustion engine, i.e. for four-stroke gasoline or diesel engines, with a first electromagnet that can be excited as a function of the operating parameters, in particular synchronously with the engine speed, and an armature that can be attracted by the first electromagnet.

Derartige Maschinen weisen je Zylinder mindestens 2 Ventile auf, die nach der derzeitig bevorzugten Technik durch Federkraft in ihre Schließstellung gedrückt und dadurch in ihre Offenstellung gebracht werden, daß auf den Ventilschaft eine der Federkraft entgegenwirkende und diese übersteigende Kraft aufgebracht wird; dies in der Art, daß auf einer von der Kurbelwelle mit der halben Drehzahl angetriebenen Hilfswelle Nocken angebracht sind, die über Kipphebel die erforderliche Kraft auf die Ventilstößel aufbringen. Nocken und Kipphebel sind durch das Aneinanderabgleiten einem erheblichen Verschleiß ausgesetzt, und der erreichbare Ventilhub ist dadurch begrenzt, daß die Flankensteigung der Nocken nicht beliebig groß gewählt werden kann, wenn die bei Zusammenwirken derselben mit den Kipphebeln aufzubringenden Kräfte nicht das zulässige Maß überschreiten sollen. Neuere Untersuchungen lassen vermuten, daß eine vollständigere Verbrennung im Zylinder und damit eine günstigere Treibstoffausnutzung und Herabsetzung der im Abgas abgegebenen Schadstoffe durch die Vergrößerung des Ventilhubs, durch ein schnelleres Öffnen und Schließen der Ventile und/oder dadurch erreichbar sein können, daß die starre Kupplung der Stellung der Ventile an diejenige des Kolbens bei allen Betriebszuständen gelockert wird. Eine solche nach Betriebszustand variable Ankopplung erfolgt bereits bei der Betätigung der Zündung bei Otto-Motoren.Such machines have at least 2 valves per cylinder, which according to the currently preferred technique are pressed into their closed position by spring force and thereby brought into their open position in that a force which counteracts and exceeds the spring force is applied to the valve stem; this in such a way that cams are mounted on an auxiliary shaft driven by the crankshaft at half the speed, which apply the required force to the valve tappets via rocker arms. The cams and rocker arms are exposed to considerable wear due to sliding against one another, and the valve lift that can be achieved is limited in that the flank pitch of the cams cannot be chosen to be as large as desired if the forces to be exerted when they interact with the rocker arms should not exceed the permissible level. Recent studies suggest that a more complete combustion in the cylinder and thus a more favorable fuel utilization and reduction of the pollutants emitted in the exhaust gas can be achieved by increasing the valve lift, by opening and closing the valves faster and / or by the rigid coupling of the Position of the valves to that of the piston is loosened in all operating conditions. Such a coupling, which is variable according to the operating state, already takes place when the ignition is actuated in Otto engines.

Elektromagnetische Ventiltriebe sind bereits bekannt, und zwar aus den DE-A 3 311 250 und EP-A 0 043 426. Hier wird versucht, das als Anker eines Elektromagneten ausgebildete Schließorgan des Ventils über den gewählten Verschiebeweg (der z.B. bei einem Kraftfahrzeugmotor von 100 KW einige mm betragen kann) durch das Erregen des ersteren zu bewegen. Dies erfordert verhältnismäßig große Elektromagneten, die nicht nur aufwendig, sondern auch oft in unmittelmarer Nähe des Motorblocks nur schwer unterzubringen sind.Electromagnetic valve trains are already known, namely from DE-A 3 311 250 and EP-A 0 043 426. Here, an attempt is made to close the valve, which is designed as an armature of an electromagnet, via the selected displacement path (for example in a motor vehicle engine of 100 KW can be a few mm) by exciting the former. This requires relatively large electromagnets, which are not only complex, but also often difficult to accommodate in the immediate vicinity of the engine block.

Aus der FR-A 932 936 sind Einrichtungen zur Betätigung von Ventilen bekannt, bei denen an den herkömmlichen Nocken einer Nockenwelle statt der Kipphebel ein erster Kolben abgleitet; dieser verdrängt Hydraulikflüssigkeit aus seinem Zylinder bzw. nimmt diese bei Rückwärtsbewegung wieder auf. Die Hydraulikflüssigkeit ihrerseits bewegt entsprechend einen zweiten Kolben, der das Ventil selbst betätigt. Dieser Schrift kann der Fachmann ferner entnehmen, daß bei der hydraulischen Übertragung auch eine Über- bzw. Untersetzung erfolgen kann, wenn die Querschnitte der beiden Kolben entsprechend unterschiedlich gewählt werden. Ein Grund, von dieser Möglichkeit Gebrauch zu machen, ergibt sich aus der Schrift jedoch nicht.From FR-A 932 936 devices for actuating valves are known in which a first piston slides on the conventional cam of a camshaft instead of the rocker arm; this displaces hydraulic fluid from its cylinder or takes it up again when moving backward. The hydraulic fluid in turn moves a second piston, which actuates the valve itself. From this document, the person skilled in the art can further see that the hydraulic transmission can also have a step-up or step-down if the cross sections of the two pistons are selected differently. However, there is no reason to use this option from the scriptures.

Die vorliegende Erfindung hat die Aufgabe, bei grundsätzlichem Festhalten an der hergebrachten Bauweise der genannten Motoren einen größeren Ventilhub zu ermöglichen und gleichzeitig verschließanfällige Teile zu eliminieren. Hierdurch soll ein günstigeres Steuerverhalten der Ventile erreicht werden.The object of the present invention is to enable a greater valve lift while basically adhering to the traditional design of the aforementioned motors and at the same time to eliminate parts which are susceptible to wear. This is intended to achieve a more favorable control behavior of the valves.

Die Lösung dieser Aufgabe ist gekennzeichnet dadurch, daß der Verschiebeweg des Ankers ca. 1-1,5 mm beträgt; durch einen ersten Kolben, der in einem ersten Hydraulikzylinder gleitet und mit dem Anker verbunden ist, einen auf den Ventilschaft wirkenden zweiten Kolben mit gegenüber dem ersten Kolben verringertem Durchmesser, der in einem zweiten Hydraulikzylinder gleitet, sowie eine den ersten und zweiten Hydraulikzylinder miteinander verbindende Leitung.The solution to this problem is characterized in that the displacement of the armature is approximately 1-1.5 mm; by a first piston which slides in a first hydraulic cylinder and is connected to the armature, a second piston which acts on the valve stem and has a reduced diameter compared to the first piston and which slides in a second hydraulic cylinder, and a line connecting the first and second hydraulic cylinders .

Dabei kann die hydraulische Kraftübertragung 1, die Bewegung des ersten Kolbens übersetzen, indem der zweite Kolben einen merklich geringeren Querschnitt aufweist als der erste Kolben. Ersterer folgt der durch letzteren aufgezwungenen Bewegung dann mit einem im Verhältnis der Querschnittsflächen vergrößerten Hub, wenn das Gesamtsystem geschlossen ist. Die Bewegung der Kolben in ihren Zylindern erfolgt wegen des Fehlens von die Gleitflächen beanspruchenden Querkräften weitgehend verschleißfrei. Da dem Anker des vorgeschlagenen ersten Elektromagneten nur ein sehr geringer Verschiebeweg in der Größenordnung von 1 bis 1,5 mm mitgeteilt zu werden braucht, reichen verhältnismäßig geringe elektromagnetische Kräfte aus. Diese geringe Bewegung wird dann durch die hydraulische Übersetzung auf den gewünschten Ventilhub vergrößert. Die Rückkehr des Ankers in seine Ausgangsstellung bei entregtem Elektromagneten kann dabei in herkömmlicher Weise durch die Kraft einer Rückstellfeder bewirkt werden.The hydraulic power transmission 1 can translate the movement of the first piston in that the second piston has a noticeably smaller cross section than the first piston. The former then follows the movement imposed by the latter with a stroke which is enlarged in relation to the cross-sectional areas when the overall system is closed. The movement of the pistons in their cylinders is largely wear-free due to the lack of transverse forces that stress the sliding surfaces. Since the armature of the proposed first electromagnet only needs to be communicated a very small displacement in the order of magnitude of 1 to 1.5 mm, relatively low electromagnetic forces are sufficient. This slight movement is then increased by the hydraulic ratio to the desired valve lift. The return of the armature to its initial position when the electromagnet is de-energized can be effected in a conventional manner by the force of a return spring.

Jedoch kann auf diese Rückstellfeder bei einer Ausgestaltung der Erfindung gemäß dem 2. Anspruch verzichtet werden, bzw. kann ihre Stärke auf das Maß herabgesetzt werden, das ausreicht, um ein mechanisches Spiel auszugleichen, wenn für jede Bewegungseinrichtung des Primärkolbens ein besonderer Elektromagnet vorhanden ist, der wechselseitig mit dem anderen erregt wird. Die Differentialkolben-Anordnung bewirkt, daß eine Verschiebung des einen Kolbens, egal in welche Richtung, stets eine entsprechende Verschiebung des anderen Kolbens zur Folge hat.However, this return spring can be dispensed with in an embodiment of the invention according to claim 2, or its strength can be reduced to the extent which is sufficient to compensate for mechanical play if a special electromagnet is present for each movement device of the primary piston, which is mutually excited with the other. The differential piston arrangement has the effect that a displacement of one piston, no matter in which direction, always results in a corresponding displacement of the other piston.

Als besonders geeignet für den Einsatz in der beschriebenen Konstruktion erscheint, wie im 3. Anspruch vorgeschlagen, ein Topfmagnet. Gemäß der im 4. Anspruch vorgeschlagenen Ausgestaltung der Erfindung können der zweite Kolben und der Ventilschaft mit dem angeformten Ventilteller aus einem Stück hergestellt sein, wodurch auch die Möglichkeit des Spiels in der Übertragung weiter vermindert wird.A pot magnet appears to be particularly suitable for use in the construction described, as proposed in claim 3. According to the embodiment of the invention proposed in claim 4, the second piston and the valve stem with the integrally formed valve plate can be made in one piece, which also further reduces the possibility of play in the transmission.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt, und zwar im Längsaxialschnitt. Die Figur zeigt teilweise den Brennraum 1 eines Zylinders einer Verbrennungskraftmaschine, dem über einen Ansaugkanal 2 ein Brennstoffluftgemisch zugeführt wird; ein Auslaßventil kann in prinzipiell gleicher Weise ausgeführt sein. Der Ansaugkanal 2 wird gegenüber dem Brennraum 1 abgeschlossen durch einen Ventilteller 4, der mit einem Stößel 5 eine Einheit bildet. Durch eine Schraubenfeder 6, die sich an einem Widerlager 7 abstützt, ist das Ventil 4 in Richtung seiner Schließstellung belastet.An embodiment of the invention is shown in the drawing, namely in the longitudinal axial section. The figure partially shows the combustion chamber 1 of a cylinder of an internal combustion engine machine to which a fuel / air mixture is supplied via an intake duct 2; an outlet valve can be designed in basically the same way. The intake duct 2 is closed off from the combustion chamber 1 by a valve disk 4, which forms a unit with a tappet 5. The valve 4 is loaded in the direction of its closed position by a helical spring 6, which is supported on an abutment 7.

Ein erster Hydraulikzylinder 13, in dem ein erster Kolben 12 gleitet, ist über zwei in Länge und Formgebung fast beliebig auszuführende Leitungen 15, 18 mit einem zweiten Hydraulikzylinder 16 verbunden, in dem ein zweiter Kolben 17 gleitet, der seinerseits auf den Ventilschaft 5 derart wirkt, daß jede Leitung jeweils auf einer Seite eines ersten bzw. zweiten Kolbens 12 bzw. 17 mündet. Ohne Rückholfeder folgt dann letzterer jeder Bewegung des ersteren. Da der von beiden Kolben 12, 17 bestrichene Hubraum gleich sein muß und der Durchmesser D des ersten Zylinders 13 größer bemessen ist als derjenige d des zweiten Zylinders 16, setzt sich die verhältnismäßig kleine hin- und hergehende Bewegung h des ersten Kolbens 12 in eine entsprechend größere Bewegung H des zweiten Kolbens 17 um. Die Größe des entsprechenden Hubs des Ventils 4 kann so über das mit Hilfe herkömmlicher Nockenwellen erzielbare Maß hinaus gesteigert werden.A first hydraulic cylinder 13, in which a first piston 12 slides, is connected to a second hydraulic cylinder 16 via two lines 15, 18 that can be designed almost arbitrarily in length and shape, in which a second piston 17 slides, which in turn acts on the valve stem 5 in this way that each line opens on one side of a first or second piston 12 or 17. Without a return spring, the latter then follows every movement of the former. Since the 17 coated displacement of the two pistons 12, must be the same and the diameter D of the first cylinder is dimensioned greater than 13 than that d of the second cylinder 16, is the relatively small back - and forth movement h of the first piston 12 in a correspondingly larger movement H of the second piston 17 by. The size of the corresponding stroke of the valve 4 can thus be increased beyond what can be achieved with the aid of conventional camshafts.

Der erste Kolben 12 ist einstückig mit einem Anker 19 ausgeführt. Der Anker 19 liegt je nach deren wechselweise vorzunehmender Erregung an einem ersten Elektromagneten 20 oder an einem zweiten Elektromagneten 21 an. Dabei ist der Luftspalt s zum jeweils entfernten Elektromagneten nur etwa 1 bis 1,5 mm groß, so daß verhältnismäßig schwache und damit kleine Elektromagneten Verwendung finden können. Dies insbesondere dann, wenn wie hier dargestellt nicht gegen eine kräftige Rückholfeder gearbeitet werden muß, sondern eine den Ventilteller 4 in seine Schließstellung drückende Feder 6 lediglich zum Spielausgleich dient und entsprechend schwach dimensioniert werden kann. Die Erregung der Elektromagneten 20, 21 erfolgt abwechselnd durch eine Steuereinheit 26, in die nicht nur die jeweilige, z. B. an einer Kurbelwelle 27 abgenommene Drehzahl der Maschine, sondern auch andere Betriebswerte eingehen, die durch hier nicht näher beschriebene Sensoren 28 erfaßt werden. Hierdurch lassen sich die dem jeweiligen Betriebszustand am genauesten entsprechenden Ventilschließzeiten steuern.The first piston 12 is made in one piece with an armature 19. The armature 19 is in contact with a first electromagnet 20 or a second electromagnet 21, depending on the alternating excitation to be carried out. The air gap s to the electromagnet removed in each case is only about 1 to 1.5 mm in size, so that relatively weak and thus small electromagnets can be used. This is particularly the case when, as shown here, it is not necessary to work against a strong return spring, but rather a spring 6, which presses the valve plate 4 into its closed position, only serves to compensate for play and can be dimensioned correspondingly weak. The excitation of the electromagnets 20, 21 takes place alternately by a control unit 26, in which not only the respective, for. B. on a crankshaft 27 decreased speed of the machine, but also other operating values that are detected by sensors 28 not described here. In this way, the valve closing times that correspond most precisely to the respective operating state can be controlled.

Claims (4)

1. Electromagnetic valve drive for a combustion engine, having a first electromagnet (20), which is excitable as a function of the operating parameters, more particularly in synchronism with the motor speed, and an armature (19) which can be attracted by the first electromagnet (20), characterised by a displacement path of the armature (19) of approximately 1-1.5 mm, a first piston (12), which sliedes in a first hydraulic cylinder (13) and is connected with the armature (19), a second piston (17) which acts on the valve shaft (5), has a diameter (d/D), diminished in relation to the first piston, and slides in a second hydraulic cylinder (16), and also a line (15) which connects the first and the second hydraulic cylinder one with the other.
2. Valve drive according to claim 1, characterised by
a) a second electromagnet (21) which is excitable in a timpe-displaced and spatially opposed manner in relation to the first electromagnet (20),
b) a second line (18) which connects the first hydraulic cylinder (13) with the second (16) and which, in relation to the first line (15), runs into the cylinder on the respective opposite side of the piston (12, 17).
3. Valve drive according to claim 1 or 2, characterised in that the first or second electromagnet (20, 21) is a pot magnet.
4. Valve drive according to claim 2, characterised in that the valve shaft (5) is integrated into the second piston (17).
EP87107613A 1985-02-11 1986-01-30 Electromagnetic-hydraulic valve drive for an internal-combustion engine Expired - Lifetime EP0244878B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87107613T ATE57989T1 (en) 1985-02-11 1986-01-30 ELECTROMAGNETIC-HYDRAULIC VALVE DRIVE FOR INTERNAL COMBUSTION ENGINES.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3504639 1985-02-11
DE19853504639 DE3504639A1 (en) 1985-02-11 1985-02-11 HYDRAULIC CONTROL FOR VALVES OF INTERNAL COMBUSTION ENGINES
DE3534388 1985-09-26
DE3534388 1985-09-26

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP86101217.7 Division 1986-01-30

Publications (3)

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EP0244878A2 EP0244878A2 (en) 1987-11-11
EP0244878A3 EP0244878A3 (en) 1987-12-23
EP0244878B1 true EP0244878B1 (en) 1990-10-31

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EP87107613A Expired - Lifetime EP0244878B1 (en) 1985-02-11 1986-01-30 Electromagnetic-hydraulic valve drive for an internal-combustion engine
EP86101217A Expired EP0191376B1 (en) 1985-02-11 1986-01-30 Valve drive with hydraulic transmission

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP86101217A Expired EP0191376B1 (en) 1985-02-11 1986-01-30 Valve drive with hydraulic transmission

Country Status (4)

Country Link
EP (2) EP0244878B1 (en)
JP (1) JPS61187505A (en)
DE (2) DE3660265D1 (en)
ES (1) ES8702577A1 (en)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
DE102005017482A1 (en) * 2005-04-15 2006-11-02 Compact Dynamics Gmbh Gas exchange valve actuator for a valve-controlled internal combustion engine
DE19723924B4 (en) * 1997-06-06 2008-02-28 Hoffmann, Bernhard Electric linear motor
US7989991B2 (en) 2005-04-15 2011-08-02 Compact Dynamics, GmbH Linear actuator

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SU1621816A3 (en) * 1987-02-10 1991-01-15 Интератом Гмбх (Фирма) Hydraulic device for controlling valves of i.c.engine
DE8717456U1 (en) * 1987-08-26 1988-12-29 INTERATOM GmbH, 5060 Bergisch Gladbach Rotary piston pump with uneven pumping performance, especially for valve control of internal combustion engines
DE3836725C1 (en) * 1988-10-28 1989-12-21 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE3920931A1 (en) * 1989-06-27 1991-01-03 Fev Motorentech Gmbh & Co Kg ELECTROMAGNETIC OPERATING DEVICE
DE4004876A1 (en) * 1990-02-16 1991-09-26 Ulrich Karrer Electrically operated valve gear for IC engine - opens and closes valve by multiplication of stroke of hydraulic piston with alternate energisation of two electromagnets
DE4020776A1 (en) * 1990-06-29 1992-01-09 Pi Patente Gmbh DEVICE FOR DRIVING A TOOL FOR AN AXIAL MOVEMENT OF THE TOOL
DE19829857A1 (en) * 1998-07-05 2000-01-13 Bayerische Motoren Werke Ag Internal combustion engine with a pneumatic and / or hydraulic actuator for a gas exchange valve
DK176152B1 (en) * 2000-07-10 2006-10-16 Man B & W Diesel As Method of activating an exhaust valve for an internal combustion engine and such an exhaust valve
AT411090B (en) * 2000-12-12 2003-09-25 Jenbacher Ag FULLY VARIABLE HYDRAULIC VALVE ACTUATOR
DE102004057574A1 (en) * 2004-11-30 2006-06-08 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Variable valve train of an internal combustion engine
WO2013000155A1 (en) * 2011-06-30 2013-01-03 Lio Pang-Chian Hydraulic remote transmission control device
CN105822377B (en) * 2016-05-04 2018-05-18 哈尔滨工程大学 Electromagnetic Control booster-type air distribution system
CN106958470A (en) * 2017-05-23 2017-07-18 海南大学 Electromagnetic hydraulic pressure valve actuating mechanism

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19723924B4 (en) * 1997-06-06 2008-02-28 Hoffmann, Bernhard Electric linear motor
DE102005017482A1 (en) * 2005-04-15 2006-11-02 Compact Dynamics Gmbh Gas exchange valve actuator for a valve-controlled internal combustion engine
DE102005017482B4 (en) * 2005-04-15 2007-05-03 Compact Dynamics Gmbh Gas exchange valve actuator for a valve-controlled internal combustion engine
US7841309B2 (en) 2005-04-15 2010-11-30 Compact Dynamics Gmbh Gas exchange valve actuator for a valve-controlled internal combustion engine
US7989991B2 (en) 2005-04-15 2011-08-02 Compact Dynamics, GmbH Linear actuator

Also Published As

Publication number Publication date
EP0244878A2 (en) 1987-11-11
ES551808A0 (en) 1986-12-16
EP0244878A3 (en) 1987-12-23
JPS61187505A (en) 1986-08-21
EP0191376B1 (en) 1988-06-01
DE3660265D1 (en) 1988-07-07
ES8702577A1 (en) 1986-12-16
EP0191376A1 (en) 1986-08-20
DE3675387D1 (en) 1990-12-06

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