EP0191376B1 - Valve drive with hydraulic transmission - Google Patents

Valve drive with hydraulic transmission Download PDF

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Publication number
EP0191376B1
EP0191376B1 EP86101217A EP86101217A EP0191376B1 EP 0191376 B1 EP0191376 B1 EP 0191376B1 EP 86101217 A EP86101217 A EP 86101217A EP 86101217 A EP86101217 A EP 86101217A EP 0191376 B1 EP0191376 B1 EP 0191376B1
Authority
EP
European Patent Office
Prior art keywords
piston
auxiliary shaft
valve
hydraulic
valve drive
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
Application number
EP86101217A
Other languages
German (de)
French (fr)
Other versions
EP0191376A1 (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
Original Assignee
Interatom Internationale Atomreaktorbau GmbH
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
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
Expired legal-status Critical Current

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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 hydraulic control for valves of internal combustion engines, i.e. of 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 n and thereby brought into their open position in that a force opposing and exceeding the spring force is applied to the valve stem; this is done 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 lifters via rocker arms.
  • Hydraulic valve drives are known, for example from DE-C-46 74 40. 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.
  • the object of the present invention is to enable a larger valve lift while at the same time adhering to the conventional design of the motors mentioned 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.
  • FIG. 1 An embodiment 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, 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.
  • a crankshaft of the machine (not shown here) with a reduction ratio of 2: 1 drives an auxiliary shaft 8 with an out-of-round cross-section (exaggerated for clarity), on which a roller 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 capable of following the deformations and material to a certain degree, based on dimensions and material, without these components being stressed beyond their elastic limit.
  • the outer race 11 is fixed in space so that it cannot follow the rotational movements of the auxiliary shaft 8 and the inner race 9 fastened thereon in the circumferential direction, but instead performs an oscillating radial movement, depending on the angular position of the auxiliary shaft 8 in question
  • Their shape is not necessarily a double oval, as shown here, but will have to be selected by the person skilled in the art depending on the desired valve timing, a shape also being possible which is not unlike that of the cams conventionally used for valve controls.
  • 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 terms of length and shape, in which a second piston 17 slides, which acts on the valve stem 5 on its part. 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 d of the second cylinder 16, the relatively small reciprocating movement h of the first piston 12 converts into a correspondingly larger movement H of the second piston 17. 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 13 distributed over its circumference, which, via the similar hydraulic transmissions described, control as many valves 4 (not shown here), in the example shown, the four intake valves of a four-cylinder engine.

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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 eine hydraulische Steuerung für Ventile von Verbrennungskraftmaschinen, d.h. von Viertakt-Otto- bzw. Dieselmotoren nach dem Oberbegriff des 1. Anspruchs. Derartige Maschinen weisen je Zylinder mindestens 2 Ventile auf, die nach der derzeitig bevorzugten Technik durch Federkraft n ihre Schliesstellung 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 Kurbewelle 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 Aneinaderabgleiten einem erhebliche 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 Herabsetung 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 - 46 74 40. 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 Hydralikkolbens etwas grösser zu bemessen als den des sekundären, passiven Kolbens und den so geförderten Uberschuss abfliessen zu lassen.The present application relates to hydraulic control for valves of internal combustion engines, i.e. of 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 n and thereby brought into their open position in that a force opposing and exceeding the spring force is applied to the valve stem; this is done 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 lifters via rocker arms. The cams and rocker arms are subject to considerable wear due to sliding against one another, 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 of any size 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 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 on that of the piston is loosened in all operating states. Such a coupling, which is variable according to the operating state, already takes place when the ignition is activated in Otto engines. Hydraulic valve drives are known, for example from DE-C-46 74 40. 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.

Die vorliegende Erfindung hat die Aufgabe, bei grundsätzlichem Festhalten an der hergebrachten Bauweise der genannten Motoren einen grösseren Ventilhub zu ermögliche und gleichzeitig verschleissanfällige Teile zu eliminieren. Hierdurch soll ein günstigeres Steuerverhalten der Ventile erreicht werden.The object of the present invention is to enable a larger valve lift while at the same time adhering to the conventional design of the motors mentioned 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 1. Anspruchs agegebenen Mittel.This problem is solved by the means specified in the characterizing part of the first claim.

Die Bewegung der Kolben in ihren Zylindern erfolgt wegen des Fehlens von die Gleitflächen beanspruchenden Querkräften weitgehend verschleissfrei. Wird ein Wälzlager, dessen Laufringe durch Herbsetzung der Materialstärken und Auswahl geeingneter Werkstoffe im makroskopischen Bereich elastisch verformbar sind, 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 hydralisch übertragen, wobei zwischen Lageraussenring und dem Primärkolben keine Relativbewegung und somit kein Verschleiss auftritt.The movement of the pistons in their cylinders is largely free of wear due to the absence of transverse forces which stress the sliding surfaces. If a rolling bearing whose races can be elastically deformed in the macroscopic range by reducing the material thickness and selecting suitable materials, the inner race adjusts to this contour and is forced by the practically non-deformable rolling elements, including the outer race. If the shaft rotates relative 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 race of the bearing and the primary piston.

Gemäss dem 2. 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 claim 2, 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.

Ein Ausführungsbeispiel ist in der Zeichnung dargestellt, und zwar im Längsaxialschnitt. Die Figur zeigtteilweise 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 eine 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 ässeren Laufrig 11. Die Laufringe 9, 11 sind nach Abmessungen und Werkstoff in der Lage, ihnen aufgewungenen Verformungen bis zu einem gewissen Grade zu folgen, ohne dass 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 dargestellt, 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 Hydraulikylinder 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 seinrseits 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 d des zweiten Zylinders 16, setzt sich die verhältnismässig kleine hin-und hergehende Bewegung h des ersten Kolbens 12 in eine 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.An embodiment 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, 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. A crankshaft of the machine (not shown here) with a reduction ratio of 2: 1 drives an auxiliary shaft 8 with an out-of-round cross-section (exaggerated for clarity), on which a roller 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 capable of following the deformations and material to a certain degree, based on dimensions and material, 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 cannot follow the rotational movements of the auxiliary shaft 8 and the inner race 9 fastened thereon in the circumferential direction, but instead performs an oscillating radial movement, depending on the angular position of the auxiliary shaft 8 in question Their shape is not necessarily a double oval, as shown here, but will have to be selected by the person skilled in the art depending on the desired valve timing, a shape also being possible which is not unlike that of the cams conventionally used for valve controls. 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 terms of length and shape, in which a second piston 17 slides, which acts on the valve stem 5 on its part. 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 d of the second cylinder 16, the relatively small reciprocating movement h of the first piston 12 converts into a correspondingly larger movement H of the second piston 17. 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 13, die über der beschriebenen gleichartige hydraulische Übertragungen ebensoviele hier nicht dargestellte Ventile 4, im dargestellten Beispiel die vier Einlassventile eines Vier-Zylinder-Motores steuern.As indicated, the outer race 11 simultaneously actuates a plurality of first pistons 13 distributed over its circumference, which, via the similar hydraulic transmissions described, control as many valves 4 (not shown here), in the example shown, the four intake valves of a four-cylinder engine.

Claims (2)

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 cylider (16) and also a line (15) which connects the first and the second hydraulic cylinder one with the other, characterised in that secured on the auxiliary shaft (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.
2. Control according to claim 1, characterised in that the first piston (12) has a greater cross section than the second piston (17).
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

Publications (2)

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

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ID=25829292

Family Applications (2)

Application Number Title Priority Date Filing Date
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 Before (1)

Application Number Title Priority Date Filing Date
EP87107613A Expired - Lifetime EP0244878B1 (en) 1985-02-11 1986-01-30 Electromagnetic-hydraulic valve drive for an internal-combustion engine

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

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
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
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
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

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR471102A (en) * 1913-10-02 1914-10-15 Ettore Bugatti Hydraulic motor control with adjusting piston forming compensator
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
DE467440C (en) * 1927-05-08 1928-10-25 Waggon Und Maschb Akt Ges Goer Pressure fluid control for valves of internal combustion engines
FR932936A (en) * 1946-07-31 1948-04-06 Improvement in hydraulic controls of engine components and various machines
FR941789A (en) * 1947-01-16 1949-01-20 Hydraulic valve actuator
US2635544A (en) * 1948-03-06 1953-04-21 Lossau Earl Hydraulic valve lifting mechanism
DE1002563B (en) * 1951-07-09 1957-02-14 Gerhard Schaller Hydraulic valve drive for internal combustion engines
FR1380557A (en) * 1963-10-02 1964-12-04 Glaenzer Spicer Sa Journal
DE2057639A1 (en) * 1969-12-05 1971-06-24 Inst Regelungstechnik Digital hydraulic actuator
GB1591421A (en) * 1977-01-12 1981-06-24 Lucas Industries Ltd Valve operating mechanism
DE2907033A1 (en) * 1979-02-23 1980-09-04 Bosch Gmbh Robert IC engine gas change valve actuator - is of hydraulically controlled type energised by electro-fluidic transducer via control line
DE3024109A1 (en) * 1980-06-27 1982-01-21 Pischinger, Franz, Prof. Dipl.-Ing. Dr.Techn., 5100 Aachen ELECTROMAGNETIC OPERATING DEVICE
DE3046891A1 (en) * 1980-12-12 1982-07-15 Robert Bosch Gmbh, 7000 Stuttgart ELECTROMAGNET
GB2122257B (en) * 1982-06-04 1986-04-16 Paul Julian Moloney Valve operating mechanism for internal combustion and like-valved engines
DE3311250C2 (en) 1983-03-28 1985-08-01 FEV Forschungsgesellschaft für Energietechnik und Verbrennungsmotoren mbH, 5100 Aachen Device for the electromagnetic actuation of a gas exchange valve for positive displacement machines

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
DE3660265D1 (en) 1988-07-07
ES8702577A1 (en) 1986-12-16
EP0191376A1 (en) 1986-08-20
DE3675387D1 (en) 1990-12-06

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