EP0191376A1 - Valve drive with hydraulic transmission - Google Patents

Valve drive with hydraulic transmission Download PDF

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Publication number
EP0191376A1
EP0191376A1 EP86101217A EP86101217A EP0191376A1 EP 0191376 A1 EP0191376 A1 EP 0191376A1 EP 86101217 A EP86101217 A EP 86101217A EP 86101217 A EP86101217 A EP 86101217A EP 0191376 A1 EP0191376 A1 EP 0191376A1
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EP
European Patent Office
Prior art keywords
piston
valve
cylinder
electromagnet
valve train
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.)
Granted
Application number
EP86101217A
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German (de)
French (fr)
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EP0191376B1 (en
Inventor
Gabriel Dipl.-Ing. Tittizer
Ewald Dipl.-Ing. Junghans
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.)
Interatom Internationale Atomreaktorbau GmbH
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Interatom Internationale Atomreaktorbau GmbH
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Publication date
Priority claimed from DE19853504639 external-priority patent/DE3504639A1/en
Application filed by Interatom Internationale Atomreaktorbau GmbH filed Critical Interatom Internationale Atomreaktorbau GmbH
Priority to AT86101217T priority Critical patent/ATE34803T1/en
Publication of EP0191376A1 publication Critical patent/EP0191376A1/en
Application granted granted Critical
Publication of EP0191376B1 publication Critical patent/EP0191376B1/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 a valve train for internal combustion engines, ie for four-stroke gasoline or diesel engines according to the preamble of claim 1.
  • 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.
  • Hydraulic valve drives are known, for example from DE-C-467 440. This results in greater freedom of movement in the coupling between the crankshaft and the closing element of the valve. In order to compensate for losses of hydraulic fluid and to prevent the occurrence of air bubbles in the system, this document suggests that the displacement of the primary, active hydraulic piston be dimensioned somewhat larger than that of the secondary, passive piston and the excess conveyed in this way.
  • Electromagnetic valve drives are also already known, namely from DE-A-33 .11 250 and 30 24 109.
  • 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.
  • the object of the present invention is to allow a larger valve lift while at the same time adhering to the conventional construction 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 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 follows the movement imposed by the latter with a stroke which is enlarged in the ratio of the cross-sectional areas when the overall system is closed.
  • This return spring can be dispensed with in an embodiment of the invention according to the fifth claim, or its strength can be reduced to the extent that is sufficient to compensate for mechanical play.
  • 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.
  • 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 partially shows the combustion chamber 1 of a cylinder of an internal combustion engine, to which a fuel / air mixture is supplied via an intake duct 2.
  • An exhaust 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.
  • An auxiliary shaft 8 is driven by a crankshaft of the machine (not shown here) with a reduction ratio of 2: 1 (exaggerated here for clarification) ) non-circular cross-section on which a rolling bearing is attached.
  • the rolling bearing consists in a known manner of an inner race 9, rolling elements 10 (balls or rollers) and an outer race 11.
  • the races 9, .11 are in terms of dimensions and material able to provide them with a certain amount of forced deformation. To be followed straight without these components being stressed beyond their elastic limit. This is the case here since the outer race 11 is fixed in space so that it.
  • Rotational movements of the auxiliary shaft 8 and the inner race 9 fastened thereon cannot follow in the circumferential direction, however performs an oscillating radial movement, depending on the angular position of the auxiliary shaft 8.
  • Its shape is not necessarily a double oval, as shown here, but will have to be selected by a person skilled in the art depending on the desired valve timing, whereby a form that is similar to that of the Cam used conventionally for valve controls is not dissimilar.
  • the movement of the outer race 11 communicates with a first piston 12, which slides in a first hydraulic cylinder 13 and is always pressed against the outer race 11 by a further helical spring 14.
  • the first hydraulic cylinder 13 is connected to a second hydraulic cylinder 16 via a line 15 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. Since the displacement swept by both pistons 12, 17 must be the same and the diameter D of the first cylinder 13 is larger than that of the second cylinder 16, the relatively small reciprocating movement h of the first piston 12 results in a correspondingly larger movement H of the second piston 17 um. 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.
  • the outer race 11 simultaneously actuates a plurality of first pistons 12 distributed over its circumference, the same number of valves 4, not shown here, via the similar hydraulic transmissions described, in the example shown the four intake valves one Control four-cylinder engine.
  • 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.
  • the first cylinder 13 is connected to the second cylinder 16 via two lines 15, 18 in such a way that each line opens on one side of the first and second piston 12 and 17, respectively. Without a return spring, the latter then follows every movement of the former.

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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)

Abstract

1. Hydraulic control for valves (4) of combustion engines having an auxiliary shaft (8) which is driven by the crankshaft and which has a non-circular cross section and, for each valve, a first piston (12) which is actuated by the auxiliary shaft and which slides in a first hydraulic cylinder (13) and a second piston (17) which is pressed against the valve stem (5) and which 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, characterized in that secured on the auxiliary shafts (8) there is a rolling bearing (9 to 11), against the outer bearing race (11) of which the first piston (12) is pressed and which is fixed in space and is strained only in the elastic region through the deformation which is forced upon it upon rotation of the auxiliary shaft.

Description

Die vorliegende Anmeldung betrifft einen Ventiltrieb für Verbrennungskraftmaschinen d. h. für Viertakt-Otto- bzw. Dieselmotoren nach den Oberbegriff des 1. Anspruchs. 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 Ankoppelung erfolgt bereits bei der Betätigung der Zündung bei Otto-Motoren. Es sind hydraulische Ventiltriebe bekannt, so aus der DE-C-467 440. Hierdurch wird eine größere Freizügigkeit in der Kopplung zwischen Kurbelwelle und Schließorgan des Ventils erreicht. Um Verluste an Hydraulikflüssigkeit auszugleichen und das Auftreten von Luftblasen im System zu verhindern schlägt diese Schrift vor, den Hubraum des primären, aktiven Hydraulikkolbens etwas größer zu bemessen als den des sekundären, passiven Kolbens und den so geförderten Überschuss abfliessen zu lassen.The present application relates to a valve train for internal combustion engines, ie for four-stroke gasoline or diesel engines according to the preamble of claim 1. 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 each other and the valve lift that can be achieved is limited by the fact 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 use of fuel and reduction of the pollutants emitted in the exhaust gas by increasing the valve lift, by faster opening and closing of the valves and / or can be achieved by loosening the rigid coupling of the position of the valves to that of the piston in all operating states. Such a coupling, which is variable according to the operating state, already occurs when the ignition is actuated in Otto engines. Hydraulic valve drives are known, for example from DE-C-467 440. This results in greater freedom of movement in the coupling between the crankshaft and the closing element of the valve. In order to compensate for losses of hydraulic fluid and to prevent the occurrence of air bubbles in the system, this document suggests that the displacement of the primary, active hydraulic piston be dimensioned somewhat larger than that of the secondary, passive piston and the excess conveyed in this way.

Auch elektromagnetische Ventiltriebe sind bereits bekannt, und zwar aus den DE-A-33 .11 250 und 30 24 109. 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 unmittelbarer Nähe des Motorblocks nur schwer unterzubringen sind.Electromagnetic valve drives are also already known, namely from DE-A-33 .11 250 and 30 24 109. 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.

Die vorliegende Erfindung hat die Aufgabe, bei grundsätzlichem Festhalten an der hergebrachten Bauweise der genannten.Motoren einen größeren Ventilhub zu ermöglichen und gleichzeitig verschleißanfällige Teile zu eliminieren. Hierdurch soll ein günstigeres Steuerverhalten der Ventile erreicht werden.The object of the present invention is to allow a larger valve lift while at the same time adhering to the conventional construction 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 erfolgt durch die im kennzeichnenden Teil des ersten Anspruchs angegebenen Mittel.This object is achieved by the means specified in the characterizing part of the first claim.

Gemäß dem zweiten Anspruch 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.According to the second claim, 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 follows the movement imposed by the latter with a stroke which is enlarged in the ratio of the cross-sectional areas when the overall system is closed.

Die Bewegung der Kolben in ihren Zylindern erfolgt wegen des Fehlens von die Gleitflächen beanspruchenden Querkräften weitgehend verschleißfrei. Wird ein Wälzlager, dessen Laufringe durch Herabsetzung der Materialstärken und Auswahl geeigneter Werstoffe im makroskopischen Bereich elastisch verformbar sind, wie im dritten Anspruch vorgeschlagen auf eine unrunde Welle aufgeschoben, so paßt sich der innere Laufring dieser Kontur an und durch die praktisch nicht verformbaren Wälzkörper gezwungen, auch der äußere Laufring. Dreht sich die Welle gegenüber dem als feststehend angenommenen äußeren Laufring, wird dem letzteren an jedem Punkte seines Umfangs eine radial hin und hergehende Bewegung aufgezwungen. Diese Bewegung wird dann hydraulisch übertragen, wobei zwischen Lageraußenring und dem Primärkolben keine Relativbewegung und somit kein Verschleiß auftritt.The movement of the pistons in their cylinders is largely wear-free due to the lack of transverse forces that stress the sliding surfaces. If a rolling bearing whose races are elastically deformable in the macroscopic range by reducing the material thickness and selecting suitable materials, as proposed in the third claim, is pushed onto an out-of-round shaft, the inner race adapts to this contour and is forced by the practically non-deformable rolling elements, also the outer race. If the shaft rotates with respect to the outer race, which is assumed to be fixed, the latter is forced to move radially back and forth at every point along its circumference. This movement is then transmitted hydraulically, with no relative movement and therefore no wear occurring between the outer bearing ring and the primary piston.

Alternativ hierzu ist die im vierten Anspruch gegebene Lösung. Dem Anker des dort vorgeschlagenen ersten Elektromagneten braucht nur ein sehr geringer Verschiebeweg in der Größenordnung von 1 bis 1,5 mm mitgeteilt werden, wozu verhältnismäßig geringe elektromagnetische Kräfte ausreichen. 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.Alternatively, there is the solution given in the fourth claim. The armature of the first electromagnet proposed there only needs to be informed of a very small displacement path of the order of 1 to 1.5 mm, for which purpose 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.

Auf diese Rückstellfeder kann bei einer Ausgestaltung der Erfindung gemäß dem fünften Anspruch verzichtet werden, bzw. kann ihre Stärke auf das Maß herabgesetzt werden, das ausreicht, um ein mechanisches Spiel auszugleichen. Für jede Bewegungseinrichtung des Primärkolbens ist ein besonderer Elektromagnet vorhanden, 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. Als besonders geeignet für den Einsatz in der beschriebenen Konstruktion erscheint, wie im sechsten Anspruch vorgeschlagen, ein Topfmagnet.This return spring can be dispensed with in an embodiment of the invention according to the fifth claim, or its strength can be reduced to the extent that is sufficient to compensate for mechanical play. For each movement device of the primary piston there is a special electromagnet 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. As proposed in the sixth claim, a pot magnet appears to be particularly suitable for use in the construction described.

Gemäß der im siebenten 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.According to the embodiment of the invention proposed in the seventh claim, 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.

Zwei Ausführungsbeispiele sind in der Zeichnung dargestellt, und zwar zeigt diese im Längsaxialschnitt in Fig. 1 eine erste, rein mechanisch-hydraulische Ausführung und Fig. 2 eine zweite, elektromagnetische hydraulisch-mechanische Ausführung. Die Fig. 1 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, Von einer hier nicht dargestellten Kurbelwelle der Maschine mit einem Untersetzungsverhältnis von 2:1 angetrieben ist eine Hilfswelle 8 mit (hier zur Verdeutlichung Übertrieben dargestelltem) unrundem Querschnitt vorhanden, auf der ein Wälzlager befestigt ist. Das Wälzlager besteht in bekannter Weise aus einem inneren Laufring 9, Wälzkörpern 10 (Kugeln oder Rollen) und einem äußeren Laufring 11. Die Laufringe 9,.11 sind nach Abmessungen und Werkstoff in der Lage, ihnen auf gezwungenen Verformungen bis zu einem gewissen. Grade zu folgen, ohne uaß diese Bauteile über ihre Elastizitätsgrenze hinweg beansprucht würden. Dies ist hier der Fall, da der äußere Laufring 11 im Raum fixiert ist, so daß er. Drehbewegungen der Hilfswelle 8. und des darauf befestigten inneren Laufringes 9 in Umfangsrichtung nicht folgen kann, dagegen eine oszillierende Radialbewegung ausführt, je nach der betreffenden Winkellage der Hilfswelle 8. Deren Gestalt ist nicht notwendigerweise, wie hier dargestellte eine doppelt-ovigale sondern wird vom Fachmann je nach den angestrebten Ventilsteuerzeiten auszuwählen sein, wobei auch eine Form in Frage kommt, die derjenigen der herkömmlich für Ventilsteuerungen verwendeten Nocken nicht unähnlich ist. Die Bewegung des äußeren Laufringes 11 teilt sich einem ersten Kolben 12 mit, der in einem ersten Hydraulikzylinder 13 gleitet und durch eine weitere Schraubenfeder 14 stets gegen den äußeren Laufring 11 gedrückt wird. Der erste Hydraulikzylinder 13 ist über eine in Länge und Formgebung fast beliebig auszuführende Leitung 15 mit einem zweiten Hydraulikzylinder 16 verbunden, in dem ein zweiter Kolben 17 gleitet, der seinerseits auf den Ventilschaft 5 wirkt. 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 ddeszweiten 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.Two exemplary embodiments are shown in the drawing, namely in longitudinal axial section in FIG. 1 a first, purely mechanical-hydraulic version and FIG. 2 a second, electromagnetic hydraulic-mechanical version. 1 partially shows the combustion chamber 1 of a cylinder of an internal combustion engine, to which a fuel / air mixture is supplied via an intake duct 2. An exhaust 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. An auxiliary shaft 8 is driven by a crankshaft of the machine (not shown here) with a reduction ratio of 2: 1 (exaggerated here for clarification) ) non-circular cross-section on which a rolling bearing is attached. The rolling bearing consists in a known manner of an inner race 9, rolling elements 10 (balls or rollers) and an outer race 11. The races 9, .11 are in terms of dimensions and material able to provide them with a certain amount of forced deformation. To be followed straight without these components being stressed beyond their elastic limit. This is the case here since the outer race 11 is fixed in space so that it. Rotational movements of the auxiliary shaft 8 and the inner race 9 fastened thereon cannot follow in the circumferential direction, however performs an oscillating radial movement, depending on the angular position of the auxiliary shaft 8. Its shape is not necessarily a double oval, as shown here, but will have to be selected by a person skilled in the art depending on the desired valve timing, whereby a form that is similar to that of the Cam used conventionally for valve controls is not dissimilar. The movement of the outer race 11 communicates with a first piston 12, which slides in a first hydraulic cylinder 13 and is always pressed against the outer race 11 by a further helical spring 14. The first hydraulic cylinder 13 is connected to a second hydraulic cylinder 16 via a line 15 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. Since the displacement swept by both pistons 12, 17 must be the same and the diameter D of the first cylinder 13 is larger than that of the second cylinder 16, the relatively small reciprocating movement h of the first piston 12 results in a correspondingly larger movement H of the second piston 17 um. 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.

Wie angedeutet, betätigt der äußere Laufring 11 gleichzeitig mehrere über seinen Umfang verteilte erste Kolben 12, die über der beschriebenen gleichartige hydraulische Übertragungen ebensoviele hier nicht dargestellte Ventile 4, im dargestellten Beispiel die vier Einlaßventile eines Vier-Zylinder-Motors steuern.As indicated, the outer race 11 simultaneously actuates a plurality of first pistons 12 distributed over its circumference, the same number of valves 4, not shown here, via the similar hydraulic transmissions described, in the example shown the four intake valves one Control four-cylinder engine.

In der Fig. 2 ist der erste Kolben 12 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, sodaß 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. Hier ist der erste Zylinder 13 über zwei Leitungen 15, 18 mit dem zweiten Zylinder 16 verbunden derart, daß jede Leitung jeweils auf einer Seite des ersten bzw. zweiten Kolbens 12 bzw. 17 mündet. Ohne Rückholfeder folgt dann letzterer jeder Bewegung des ersteren.2, 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. Here, the first cylinder 13 is connected to the second cylinder 16 via two lines 15, 18 in such a way that each line opens on one side of the first and second piston 12 and 17, respectively. Without a return spring, the latter then follows every movement of the former.

Claims (7)

1. Ventiltrieb für Verbrennungskraftmaschinen mit einer hydraulischen Übertragung zwischen Steuerorgan (8, 20, 21) und Ventil (4), dadurch gekennzeichnet, daß die hydraulische Übertragung eine Übersetzung aufweist.1. Valve train for internal combustion engines with a hydraulic transmission between the control member (8, 20, 21) and valve (4), characterized in that the hydraulic transmission has a translation. 2. Ventiltrieb nach Anspruch 1, mit je Vientil (4) einem ersten Zylinder (13), in dem ein erster, durch das Steuerorgan (8, 20, 21) bewegbarer Kolben (12) gleitet und einemzweiten über eine oder mehrere Leitungen (15, 18) dicht mit dem ersten verbundenen zweiten Zylinder (16), in dem ein zweiter Kolben (17) gleitet, durch den das Ventil bewegbar ist, wobei der Durchmesser D des ersten Zylinders größer ist als der Durchmesser d des zweiten Zylinders,
dadurch gekennzeichnet,
daß die Zylinder (13, 16) und Leitungen (15, 18) ein geschlossenes System bilden.2. Valve train according to claim 1, with each valve (4) a first cylinder (13) in which a first piston (12, 20, 21) movable by the control member (8) slides and a second one or more lines (15) , 18) tightly connected to the first connected second cylinder (16), in which a second piston (17) slides, through which the valve can be moved, the diameter D of the first cylinder being larger than the diameter d of the second cylinder,
characterized,
that the cylinders (13, 16) and lines (15, 18) form a closed system. 3. Ventiltrieb nach Anspruch 2 mit einer von der Kurbelwelle aus angetriebenen Hilfswelle (8), die auf einem Teil ihrer Länge einen unrunden Querschnitt aufweist, gekennzeichnet durch ein auf einer Hilfswelle (8) befestigtes Wälzlager (9, 10, 11), dessen äußerer Laufring (11) im Raum fixiert ist und durch die bei Drehung der Hilfswelle ihm aufgezwungene Verformung nur im elastischen Bereich beansprucht wird, wobei der erste Kolben gegen den äußeren Laufring (11) gepreßt ist.3. Valve train according to claim 2 with a crankshaft driven auxiliary shaft (8), which has a non-circular cross-section over part of its length, characterized by a roller bearing (9, 10, 11) attached to an auxiliary shaft (8), the outer one The race (11) is fixed in space and due to the deformation forced upon rotation of the auxiliary shaft, it is only stressed in the elastic range, the first piston being pressed against the outer race (11). 4. Ventiltrieb nach Anspruch 2, gekennzeichnet durch , a) einen in Abhängigkeit von den Betriebsparametern, insbesondere synchron zur Motordrehzahl erregbaren ersten Elektromagneten (20), b) einen durch den ersten Elektromagneten (20) anziehbaren Anker (19), der mit dem ersten Kolben (12) verbunden ist. 4. Valve train according to claim 2, characterized by a) a first electromagnet (20) which can be excited as a function of the operating parameters, in particular synchronously with the engine speed, b) an armature (19) which can be attracted by the first electromagnet (20) and which is connected to the first piston (12). 5. Ventiltrieb nach Anspruch 4, gekennzeichnet durch , a) einen zweiten Elektromagneten (21), der zeitlich versetzt und räumlich entgegengesetzt zum ersten Elektromagneten (20) erregbar ist, b) eine zweite den ersten (10) mit dem zweiten Zylinder (7) verbindende Leitung (18), die tin Bezug auf die erste Leitung (15) jeweils auf der entgegengesetzten Seite des Kolbens (12, 17) in den Zylinder mündet. 5. Valve train according to claim 4, characterized by a) a second electromagnet (21) which can be excited at different times and spatially opposite to the first electromagnet (20), b) a second to first (10) connecting with the second cylinder (7) line (18), the ti n with respect to the first line (15) each on the opposite side of the piston (12, 17) opens into the cylinder. 6. Ventiltrieb nach Anspruch 4 bzw. 5,
dadurch gekennzeichnet,
daß der erste oder zweite Elektromagnet (20, 21) ein Topfmagnet ist.6. Valve train according to claim 4 or 5,
characterized,
that the first or second electromagnet (20, 21) is a pot magnet. 7. Ventiltrieb nach Anspruch 2,
dadurch gekennzeichnet,
daß der Ventilschaft (5) in den zweiten Kolben (6) integriert ist.7. Valve train according to claim 2,
characterized,
that the valve stem (5) is integrated in the second piston (6).
EP86101217A 1985-02-11 1986-01-30 Valve drive with hydraulic transmission Expired EP0191376B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86101217T ATE34803T1 (en) 1985-02-11 1986-01-30 VALVE GEAR WITH HYDRAULIC GAIN.

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 Child Applications (1)

Application Number Title Priority Date Filing Date
EP87107613.9 Division-Into 1986-01-30

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EP0191376A1 true EP0191376A1 (en) 1986-08-20
EP0191376B1 EP0191376B1 (en) 1988-06-01

Family

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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

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

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JP (1) JPS61187505A (en)
DE (2) DE3660265D1 (en)
ES (1) ES8702577A1 (en)

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EP0306735A1 (en) * 1987-08-26 1989-03-15 INTERATOM Gesellschaft mit beschränkter Haftung Valve control for an internal-combustion engine by means of a rotary-piston pump using an intermittent flow rate
US4821689A (en) * 1987-02-10 1989-04-18 Interatom Gmbh Valve drive with a hydraulic transmission and a characteristic variable by means of a link control
CN1329635C (en) * 2000-07-10 2007-08-01 曼B与W狄赛尔公司 Method for driving exhaust valve in internal combustion engine and exhaust valve thereof
CN105822377A (en) * 2016-05-04 2016-08-03 哈尔滨工程大学 Electromagnetic control booster-type valve system
CN106958470A (en) * 2017-05-23 2017-07-18 海南大学 Electromagnetic hydraulic pressure valve actuating mechanism

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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
DE19723924B4 (en) * 1997-06-06 2008-02-28 Hoffmann, Bernhard Electric linear motor
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
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
DE102005017482B4 (en) 2005-04-15 2007-05-03 Compact Dynamics Gmbh Gas exchange valve actuator for a valve-controlled internal combustion engine
DE102005017481B4 (en) 2005-04-15 2007-08-30 Compact Dynamics Gmbh Linear Actuator
WO2013000155A1 (en) * 2011-06-30 2013-01-03 Lio Pang-Chian Hydraulic remote transmission control device

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FR573596A (en) * 1922-10-02 1924-06-26 Improvements made to the control of certain elements, in periodic movement, of engines, in particular that of elements, such as valves, injection devices and lubrication devices, the movement of which alternates with periods of rest
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DE1002563B (en) * 1951-07-09 1957-02-14 Gerhard Schaller Hydraulic valve drive for internal combustion engines
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US4821689A (en) * 1987-02-10 1989-04-18 Interatom Gmbh Valve drive with a hydraulic transmission and a characteristic variable by means of a link control
EP0306735A1 (en) * 1987-08-26 1989-03-15 INTERATOM Gesellschaft mit beschränkter Haftung Valve control for an internal-combustion engine by means of a rotary-piston pump using an intermittent flow rate
US4896633A (en) * 1987-08-26 1990-01-30 Interatom Gmbh Valve control of internal combustion engines by means of a rotary piston pump with unequal pumping output
CN1329635C (en) * 2000-07-10 2007-08-01 曼B与W狄赛尔公司 Method for driving exhaust valve in internal combustion engine and exhaust valve thereof
CN105822377A (en) * 2016-05-04 2016-08-03 哈尔滨工程大学 Electromagnetic control booster-type valve system
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

Also Published As

Publication number Publication date
EP0244878A2 (en) 1987-11-11
EP0244878B1 (en) 1990-10-31
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
DE3675387D1 (en) 1990-12-06

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