EP1375843B1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
EP1375843B1
EP1375843B1 EP02450145A EP02450145A EP1375843B1 EP 1375843 B1 EP1375843 B1 EP 1375843B1 EP 02450145 A EP02450145 A EP 02450145A EP 02450145 A EP02450145 A EP 02450145A EP 1375843 B1 EP1375843 B1 EP 1375843B1
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EP
European Patent Office
Prior art keywords
valve
internal combustion
cam
combustion engine
hydraulic
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
EP02450145A
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German (de)
French (fr)
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EP1375843A1 (en
Inventor
Johannes Rieger
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AVL List GmbH
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AVL List GmbH
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Publication date
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Priority to DE50200400T priority Critical patent/DE50200400D1/en
Priority to EP02450145A priority patent/EP1375843B1/en
Publication of EP1375843A1 publication Critical patent/EP1375843A1/en
Application granted granted Critical
Publication of EP1375843B1 publication Critical patent/EP1375843B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0047—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other
    • 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
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column

Definitions

  • the invention relates to an internal combustion engine with at least one cylinder and with at least one gas exchange valve, which is controlled by a first camshaft via a first cam and by a second camshaft via a second cam, at least one camshaft for changing the timing of the gas exchange valve in its phase position is adjustable.
  • EP 0 596 860 A discloses a method and a device for changing the valve timing, in which each cam is composed of two half-cams which can be rotated relative to one another. In this way it is possible to change the valve opening duration.
  • an inner shaft is provided within a hollow-drilled camshaft and can be rotated with respect to the camshaft. In this way, both the start of the valve opening and the end of the valve opening can be set independently of one another within certain limits, but the valve lift is still predetermined, and the device is also complex and expensive.
  • An internal combustion engine according to the preamble of claim 1 is known from WO 0 248 510 A.
  • the object of the present invention is to provide an internal combustion engine with a valve control which avoids these disadvantages and allows great degrees of freedom in the setting of the valve opening times and in the lifting height of the valve movement.
  • the mechanical effort should be as low as possible so that cost-effective production and maintenance can be achieved.
  • Another object of the invention is to provide a solution in which a valve shutdown can also be implemented in a simple manner if this is necessary.
  • the first cam acts on a first hydraulic member and the second cam acts on a second hydraulic member, which two hydraulic members act together on a third hydraulic member which actuates the gas exchange valve.
  • the switching of the hydraulic elements is carried out in such a way that the gas exchange valve only opens when there is an actuation by the first cam and the second cam at the same time.
  • the cam contours are designed such that, for example, the first cam acts on the first hydraulic element before the earliest possible valve opening time. This means that only the second cam causes the actual valve opening.
  • the second cam is in turn designed such that it still acts on the second hydraulic member even at the latest possible valve closing time, so that the valve is closed when the first cam ends the application of the first hydraulic member.
  • valve lift can also be reduced in a simple manner.
  • the full advantages of the invention are only achieved when the two camshafts can be adjusted independently of one another.
  • a structurally particularly favorable solution of the invention is provided if the first cam acts on the respective hydraulic member via a first rocker arm and the second cam via a second rocker arm.
  • a particularly simple construction can be achieved if the first rocker arm and the second rocker arm are mounted on a common axis.
  • one of the rocker arms has a preferably adjustable driver for the other rocker arm, as a result of which the latter is actuated when the latter is not actuated.
  • the setting can be implemented, for example, by a screw on the driver, which makes it possible to change the coordination of the rocker arms accordingly.
  • a valve shutdown can be implemented in a simple manner in that the gas exchange valve is opened only when a switching valve is provided which is designed to prevent the gas exchange valve from being actuated.
  • the present invention is basically suitable for all types of internal combustion engines, that is to say in particular also for internal combustion engines with spark ignition and those with auto-ignition.
  • the valve control according to the invention can control both an inlet valve and an outlet valve, or both inlet valves and outlet valves can be variably controlled independently of one another.
  • a particularly simple embodiment of the internal combustion engine is achieved if the gas exchange valve, which is controlled by the first camshaft and by the second camshaft, is an intake valve and that an exhaust valve is controlled by the first camshaft.
  • the gas exchange valve which is controlled by the first camshaft and by the second camshaft, is an intake valve and that an exhaust valve is controlled by the first camshaft.
  • two camshafts can be used to control the intake and exhaust valves.
  • the control times of the exhaust valve are firmly coupled with the opening or the closing movement of the intake valve.
  • the third hydraulic element acts on a valve bridge for actuating a plurality of gas exchange valves of the same type. In this way, for example, two inlet valves can be opened and closed simultaneously.
  • a further optimization of the present invention can be achieved in that the hydraulic device comprising the hydraulic members comprises a valve play compensation device. Due to the leakage of the system, the functionality of valve clearance compensation is achieved without a noticeable increase in effort. In this way, the additional effort compared to a conventional internal combustion engine with valve clearance compensation can be kept within manageable limits.
  • a gas exchange valve 1 which can be an inlet valve or an outlet valve, is assigned to a cylinder (not shown in more detail).
  • the gas exchange valve 1 is biased into the closed position by a valve spring 2, which is supported on a plate 3.
  • a hydraulic piston 5 is movably mounted in a housing 4, which represents the third hydraulic member and acts on the gas exchange valve 1 via a piston rod 6 in order to open the latter.
  • the hydraulic piston 5 delimits a working space 7 which is in flow connection with a first hydraulic cylinder 8 and a second hydraulic cylinder 9.
  • a first and a second control piston 10, 11 are each movably arranged in the first and second hydraulic cylinders 8, 9.
  • the first piston 10 is actuated by a first rocker arm 12, which in turn is actuated by a first cam 14 which is arranged on a first camshaft 16.
  • the second piston 11 is actuated by a second rocker arm 13 and a second cam 15 on a second camshaft 17.
  • the first and the second rocker arms 12, 13 are mounted on a common axis 18.
  • the first rocker arm 12 has an integrally formed driver 19 which actuates the second rocker arm 13 when the first rocker arm 12 is not actuated.
  • the working space 7 and the associated cylinder spaces 8, 9 are connected to a switching valve 21 via a connecting line 20.
  • the connecting line 20 is supplied with engine oil from the engine oil circuit via a supply line 22 in which a check valve 23 is provided.
  • a foreign oil supply is also possible possible.
  • the variability of the valve train according to the invention is shown using a diagram.
  • the valve stroke h is plotted in arbitrary units over the crank angle KW.
  • 30 designates a first curve section, which corresponds to an early opening of the gas exchange valve 1.
  • the curve section 30 continues in the curve sections 31, 32 or 33, with 31 corresponding to a very early closing, 32 a medium closing and 33 a late closing.
  • the maximum valve lift h is not reached, since the closing movement begins before the opening movement is completed.
  • further curves 40, 41, 42 and 43 are entered with broken lines, which correspond to curves 30, 31, 32 and 33, but with a later valve opening time.
  • the length of the valve opening and the stroke corresponding to curves 41, 42 and 43 are identical to those in the case of curves 31, 32 and 33, respectively.
  • the curve 51 represents the elevation of the first cam 14, which alternates between n 0 , the base circle, and n 1 , the cam elevation.
  • the curve 52 represents the situation on the second cam 15, which changes between the basic position m 0 and the raised position m 1 .
  • t 0 which corresponds to a crank angle of 0 °
  • the first cam 14 is in the raised position n 1
  • the second cam 15 is in the basic position m 0 . Accordingly, the gas exchange valve 1 is in its closed position.
  • the rising edge begins at second cam 15, which continues until time t 2 , in which second cam 15 has reached the raised position m 1 .
  • This time period between t 1 and t 2 corresponds to the opening movement of the gas exchange valve 1.
  • both cams 14, 15 remain in the raised position n 1 , m 1 , and the gas exchange valve 1 remains completely open.
  • the first cam 14 sinks to its base circle at n 0 , and accordingly the gas exchange valve 1 closes and is completely closed from time t 4 .
  • the descending flank of the second cam 15 begins at an arbitrary point in time t 5 , which in any case must be after the latest possible point in time t 4 , as can be seen from curve 52.
  • the driver 19 of the first rocker arm 12 holds down the second rocker arm 13, it lifts off the second cam 15, so that a fictitious cam curve 53 results, which is shown with dash-dotted lines is shown.
  • the time t 6 corresponds to the reaching of the base circle of the second cam 15, but this is meaningless for the system.
  • Only at a point in time t 7 does the rising flank of the first cam 14 begin with a corresponding movement of the first rocker arm 12, as a result of which the driver 19 accordingly releases the second rocker arm 13 until it finally rests on the second cam 15.
  • time t 8 which corresponds to 720 ° crank angle, this movement has ended and a new work cycle begins at t 0 .
  • the present invention makes it possible in a simple manner to determine the valve timing with large degrees of freedom.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Die Erfindung betrifft eine Brennkraftmaschine mit innerer Verbrennung mit mindestens einem Zylinder und mit mindestens einem Gaswechselventil, das durch eine erste Nockenwelle über einen ersten Nocken und durch eine zweite Nockenwelle über einen zweiten Nocken gesteuert ist, wobei mindestens eine Nockenwelle zur Veränderung der Steuerzeiten des Gaswechselventils in ihrer Phasenlage verstellbar ausgeführt ist.The invention relates to an internal combustion engine with at least one cylinder and with at least one gas exchange valve, which is controlled by a first camshaft via a first cam and by a second camshaft via a second cam, at least one camshaft for changing the timing of the gas exchange valve in its phase position is adjustable.

Es ist bekannt, dass Brennkraftmaschinen mit innerer Verbrennung optimiert werden können, indem die Ventilsteuerzeiten der Einlass- und Auslassventile in Abhängigkeit von dem jeweiligen Betriebszustand verändert werden.It is known that internal combustion engines can be optimized by changing the valve timing of the intake and exhaust valves depending on the respective operating state.

Durch eine solche Maßnahme kann sowohl die Leistung erhöht werden, als auch Kraftstoffverbrauch und die Abgasemissionen verringert werden. Eine bekannte Möglichkeit, eine solche Veränderung der Ventilsteuerzeiten zu realisieren, besteht darin, die Nockenwelle, die die Betätigung des betreffenden Ventils vornimmt, gegenüber einer Normalstellung geringfügig zu verdrehen. Es ist klar, dass auf diese Weise die Dauer der Ventilöffnung und der Ventilhub bei der Öffnung unveränderlich sind.Such a measure can both increase performance and also reduce fuel consumption and exhaust gas emissions. A known possibility of realizing such a change in the valve timing is to slightly rotate the camshaft that actuates the valve in question in relation to a normal position. It is clear that in this way the duration of the valve opening and the valve lift upon opening are invariable.

Aus der EP 0 596 860 A ist ein Verfahren und eine Vorrichtung zur Veränderung der Ventilsteuerzeiten bekannt, bei denen sich jeder Nocken aus zwei Halbnocken zusammensetzt, die gegeneinander verdrehbar sind. Auf diese Weise ist es möglich, auch die Ventilöffnungsdauer zu verändern. Um die Halbnocken unabhängig voneinander verstellen zu können, ist innerhalb einer hohl gebohrten Nockenwelle eine Innenwelle vorgesehen, die gegenüber der Nockenwelle verdrehbar ist. Auf diese Weise können zwar sowohl der Beginn der Ventilöffnung als auch das Ende der Ventilöffnung innerhalb gewisser Grenzen unabhängig voneinander eingestellt werden, aber der Ventilhub ist nach wie vor vorgegeben, und außerdem ist die Vorrichtung komplex und aufwendig.EP 0 596 860 A discloses a method and a device for changing the valve timing, in which each cam is composed of two half-cams which can be rotated relative to one another. In this way it is possible to change the valve opening duration. In order to be able to adjust the half-cams independently of one another, an inner shaft is provided within a hollow-drilled camshaft and can be rotated with respect to the camshaft. In this way, both the start of the valve opening and the end of the valve opening can be set independently of one another within certain limits, but the valve lift is still predetermined, and the device is also complex and expensive.

Eine weitere Lösung zur Realisierung von Ventilsteuerzeiten, bei denen Öffnungsund Schließbewegung unabhängig voneinander verändert werden können, ist in der EP 0 909 882 A beschrieben. Dabei wird ein Ventil durch zwei Nockenwellen betätigt, von denen eine im Wesentlichen die Ventilöffnungsbewegung und die andere die Ventilschließbewegung initiiert. Auch bei dieser Lösung ist nachteilig, dass der Ventilhub unveränderlich ist und dass die mechanische Komplexität groß ist.Another solution for realizing valve control times in which opening and closing movements can be changed independently of one another is described in EP 0 909 882 A. A valve is supported by two camshafts actuated, one of which essentially initiates the valve opening movement and the other initiates the valve closing movement. This solution also has the disadvantage that the valve stroke cannot be changed and that the mechanical complexity is great.

Eine Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1 ist aus WO 0 248 510 A bekannt.An internal combustion engine according to the preamble of claim 1 is known from WO 0 248 510 A.

Aufgabe der vorliegenden Erfindung ist es, eine Brennkraftmaschine mit einer Ventilsteuerung anzugeben, die diese Nachteile vermeidet und große Freiheitsgrade bei der Einstellung der Ventilöffnungszeiten und bei der Hubhöhe der Ventilbewegung ermöglicht. Dabei soll der mechanische Aufwand möglichst gering sein, so dass eine kostengünstige Herstellung und Instandhaltung erreicht werden kann. Eine weitere Aufgabe der Erfindung ist es, eine Lösung anzugeben, bei der in einfacher Weise auch eine Ventilabschaltung realisiert werden kann, sofern dies erforderlich ist.The object of the present invention is to provide an internal combustion engine with a valve control which avoids these disadvantages and allows great degrees of freedom in the setting of the valve opening times and in the lifting height of the valve movement. The mechanical effort should be as low as possible so that cost-effective production and maintenance can be achieved. Another object of the invention is to provide a solution in which a valve shutdown can also be implemented in a simple manner if this is necessary.

Diese Aufgabe wird gemäß der Erfindung mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved according to the invention with the features of claim 1.

Erfindungsgemäß ist vorgesehen, dass der erste Nocken auf ein erstes Hydraulikglied einwirkt und der zweite Nocken auf ein zweites Hydraulikglied einwirkt, welche beiden Hydraulikglieder gemeinsam auf ein drittes Hydraulikglied einwirken, das das Gaswechselventil betätigt.According to the invention, it is provided that the first cam acts on a first hydraulic member and the second cam acts on a second hydraulic member, which two hydraulic members act together on a third hydraulic member which actuates the gas exchange valve.

Wesentlich an der Erfindung ist, dass durch die Zwischenschaltung von Hydraulikgliedern, die vorzugsweise als Hydraulikzylinder ausgebildet sind, einerseits eine Vereinfachung des mechanischen Aufbaus erreicht werden kann und andererseits auch die Höhe des Ventilhubs beeinflusst werden kann.It is essential to the invention that the interposition of hydraulic elements, which are preferably designed as hydraulic cylinders, on the one hand simplifies the mechanical structure and, on the other hand, the height of the valve lift can also be influenced.

Um die Unabhängigkeit der Öffnungsbewegung des Gaswechselventils von der Schließbewegung zu erhalten, wird dabei die Schaltung der Hydraulikglieder so vorgenommen, dass das Gaswechselventil nur dann öffnet, wenn eine Betätigung durch den ersten Nocken und den zweiten Nocken gleichzeitig vorliegt. Die Nockenkonturen sind dabei so gestaltet, dass beispielsweise der erste Nocken das erste Hydraulikglied vor der frühest möglichen Ventilöffnungszeit beaufschlagt. Dies bedeutet, dass ausschließlich der zweite Nocken die tatsächliche Ventilöffnung veranlasst. Der zweite Nocken ist wiederum so ausgebildet, dass er auch noch bei dem spätest möglichen Ventilschließzeitpunkt das zweite Hydraulikglied noch beaufschlagt, so dass das Ventil geschlossen wird, wenn der erste Nocken die Beaufschlagung des ersten Hydraulikglieds beendet. Durch unabhängige Verstellung der beiden Nockenwellen können so Öffnungsund Schließbewegung des Gaswechselventils unabhängig voneinander beeinflusst werden. Wenn die Schließbewegung eingeleitet wird, bevor die Öffnungsbewegung abgeschlossen ist, kann auch der Ventilhub in einfacher Weise verringert werden. Es ist jedoch in einer vereinfachten Ausführungsvariante der Erfindung auch möglich, nur eine der beiden Nockenwellen verstellbar auszuführen, so dass beispielsweise der Ventilöffnungszeitpunkt fix ist, jedoch der Ventilschließzeitpunkt verändert werden kann. Die vollen Vorteile der Erfindung werden jedoch erst dann erreicht, wenn beide Nockenwellen unabhängig voneinander verstellbar sind.In order to maintain the independence of the opening movement of the gas exchange valve from the closing movement, the switching of the hydraulic elements is carried out in such a way that the gas exchange valve only opens when there is an actuation by the first cam and the second cam at the same time. The cam contours are designed such that, for example, the first cam acts on the first hydraulic element before the earliest possible valve opening time. This means that only the second cam causes the actual valve opening. The second cam is in turn designed such that it still acts on the second hydraulic member even at the latest possible valve closing time, so that the valve is closed when the first cam ends the application of the first hydraulic member. By independently adjusting the two camshafts, the opening and closing movements of the gas exchange valve can be influenced independently of one another. If the closing movement is initiated before the opening movement is completed, the valve lift can also be reduced in a simple manner. However, in a simplified embodiment variant of the invention, it is also possible to make only one of the two camshafts adjustable, so that, for example, the valve opening time is fixed, but the valve closing time can be changed. However, the full advantages of the invention are only achieved when the two camshafts can be adjusted independently of one another.

Eine konstruktiv besonders günstige Lösung der Erfindung ist gegeben, wenn der erste Nocken über einen ersten Kipphebel und der zweite Nocken über einen zweiten Kipphebel auf das jeweilige Hydraulikglied einwirkt. Ein besonders einfacher Aufbau kann dabei dadurch erreicht werden, wenn der erste Kipphebel und der zweite Kipphebel auf einer gemeinsamen Achse gelagert sind.A structurally particularly favorable solution of the invention is provided if the first cam acts on the respective hydraulic member via a first rocker arm and the second cam via a second rocker arm. A particularly simple construction can be achieved if the first rocker arm and the second rocker arm are mounted on a common axis.

Um sicherzustellen, dass zu jedem Zeitpunkt mindestens ein Kipphebel auf das zugehörige Hydraulikglied einwirkt, kann in bevorzugter Weise vorgesehen sein, dass einer der Kipphebel einen vorzugsweise einstellbaren Mitnehmer für den anderen Kipphebel aufweist, wodurch dieser betätigt wird, wenn jener nicht betätigt wird. Die Einstellung kann beispielsweise durch eine Schraube am Mitnehmer realisiert sein, die es ermöglicht, die Koordination der Kipphebel entsprechend zu verändern.In order to ensure that at least one rocker arm acts on the associated hydraulic member at all times, it can preferably be provided that one of the rocker arms has a preferably adjustable driver for the other rocker arm, as a result of which the latter is actuated when the latter is not actuated. The setting can be implemented, for example, by a screw on the driver, which makes it possible to change the coordination of the rocker arms accordingly.

Eine Ventilabschaltung kann in einfacher Weise dadurch realisiert werden, dass das Gaswechselventil dann und nur dann geöffnet ist, wenn ein Schaltventil vorgesehen ist, das dazu ausgebildet ist, die Betätigung des Gaswechselventils zu unterbinden.A valve shutdown can be implemented in a simple manner in that the gas exchange valve is opened only when a switching valve is provided which is designed to prevent the gas exchange valve from being actuated.

Die vorliegende Erfindung ist grundsätzlich für alle Arten von Brennkraftmaschinen, also insbesondere auch für Brennkraftmaschinen mit Fremdzündung und solche mit Selbstzündung, geeignet. Die erfindungsgemäße Ventilsteuerung kann als Gaswechselventil sowohl ein Einlassventil als auch ein Auslassventil ansteuern, oder es können sowohl Einlassventile als auch Auslassventile unabhängig voneinander variabel gesteuert werden.The present invention is basically suitable for all types of internal combustion engines, that is to say in particular also for internal combustion engines with spark ignition and those with auto-ignition. As a gas exchange valve, the valve control according to the invention can control both an inlet valve and an outlet valve, or both inlet valves and outlet valves can be variably controlled independently of one another.

Eine besonders einfache Ausführung der Brennkraftmaschine wird erreicht, wenn das Gaswechselventil, das von der ersten Nockenwelle und von der zweiten Nockenwelle gesteuert ist, ein Einlassventil ist und dass ein Auslassventil von der ersten Nockenwelle gesteuert ist. Auf diese Weise kann mit zwei Nockenwellen für die Steuerung der Ein- und Auslassventile das Auslangen gefunden werden. In diesem Fall sind die Steuerzeiten des Auslassventils fest mit der Öffnungsoder mit der Schließbewegung des Einlassventils gekoppelt.A particularly simple embodiment of the internal combustion engine is achieved if the gas exchange valve, which is controlled by the first camshaft and by the second camshaft, is an intake valve and that an exhaust valve is controlled by the first camshaft. In this way, two camshafts can be used to control the intake and exhaust valves. In this case, the control times of the exhaust valve are firmly coupled with the opening or the closing movement of the intake valve.

Bei einer Brennkraftmaschine mit drei oder mehr Ventilen pro Zylinder kann auch vorgesehen sein, dass das dritte Hydraulikglied auf eine Ventilbrücke zur Betätigung mehrerer gleichartiger Gaswechselventile einwirkt. Auf diese Weise können beispielsweise zwei Einlassventile gleichzeitig geöffnet und geschlossen werden.In an internal combustion engine with three or more valves per cylinder, it can also be provided that the third hydraulic element acts on a valve bridge for actuating a plurality of gas exchange valves of the same type. In this way, for example, two inlet valves can be opened and closed simultaneously.

Eine weitere Optimierung der vorliegenden Erfindung kann dadurch erreicht werden, dass die die Hydraulikglieder umfassende Hydraulikeinrichtung eine Ventilspielausgleichseinrichtung umfasst. Durch die Leckage des Systems wird ohne merkliche Erhöhung des Aufwandes die Funktionalität eines Ventilspielausgleichs erreicht. Auf diese Weise kann der Mehraufwand gegenüber einer herkömmlichen Brennkraftmaschine mit Ventilspielausgleich in überschaubaren Grenzen gehalten werden.A further optimization of the present invention can be achieved in that the hydraulic device comprising the hydraulic members comprises a valve play compensation device. Due to the leakage of the system, the functionality of valve clearance compensation is achieved without a noticeable increase in effort. In this way, the additional effort compared to a conventional internal combustion engine with valve clearance compensation can be kept within manageable limits.

In der Folge wird die Erfindung anhand der in den Figuren dargestellten Ausführungsvarianten näher erläutert. Es zeigen:

Fig. 1
eine Ausführungsvariante der Erfindung im Schnitt;
Fig. 2
eine axonometrische Darstellung der Ausführungsvariante von Fig. 1; und
Fig. 3 und Fig. 4
Diagramme zur Erklärung der Wirkungsweise der Erfindung.
The invention is explained in more detail below on the basis of the embodiment variants shown in the figures. Show it:
Fig. 1
an embodiment of the invention in section;
Fig. 2
an axonometric representation of the embodiment of Fig. 1; and
3 and 4
Diagrams to explain the operation of the invention.

In Fig. 1 ist der erfindungswesentliche Teil einer Brennkraftmaschine mit innerer Verbrennung dargestellt. Einem nicht näher dargestellten Zylinder ist ein Gaswechselventil 1 zugeordnet, das ein Einlassventil oder Auslassventil sein kann. In an sich bekannter Weise wird das Gaswechselventil 1 von einer Ventilfeder 2, die sich auf einem Teller 3 abstützt, in die geschlossene Stellung vorgespannt. In einem Gehäuse 4 ist ein Hydraulikkolben5 beweglich gelagert, der das dritte Hydraulikglied darstellt und über eine Kolbenstange 6 auf das Gaswechselventil 1 einwirkt, um dieses zu öffnen. Der Hydraulikkolben 5 begrenzt einen Arbeitsraum 7, der mit einem ersten Hydraulikzylinder 8 und einem zweiten Hydraulikzylinder 9 in Strömungsverbindung steht. In dem ersten bzw. zweiten Hydraulikzylinder 8, 9 ist jeweils ein erster bzw. zweiter Steuerkolben 10, 11 beweglich angeordnet. Der erste Kolben 10 wird von einem ersten Kipphebel 12 betätigt, der seinerseits von einem ersten Nocken 14 betätigt wird, der auf einer ersten Nockenwelle 16 angeordnet ist. Analog dazu wird der zweite Kolben 11 von einem zweiten Kipphebel 13 und einem zweiten Nocken 15 auf einer zweiten Nockenwelle 17 betätigt. Der erste und der zweite Kipphebel 12, 13 sind auf einer gemeinsamen Achse 18 gelagert. Der erste Kipphebel 12 besitzt einen angeformten Mitnehmer 19, der den zweiten Kipphebel 13 betätigt, wenn der erste Kipphebel 12 nicht betätigt wird.1 shows the part of an internal combustion engine essential to the invention. A gas exchange valve 1, which can be an inlet valve or an outlet valve, is assigned to a cylinder (not shown in more detail). In a manner known per se, the gas exchange valve 1 is biased into the closed position by a valve spring 2, which is supported on a plate 3. A hydraulic piston 5 is movably mounted in a housing 4, which represents the third hydraulic member and acts on the gas exchange valve 1 via a piston rod 6 in order to open the latter. The hydraulic piston 5 delimits a working space 7 which is in flow connection with a first hydraulic cylinder 8 and a second hydraulic cylinder 9. A first and a second control piston 10, 11 are each movably arranged in the first and second hydraulic cylinders 8, 9. The first piston 10 is actuated by a first rocker arm 12, which in turn is actuated by a first cam 14 which is arranged on a first camshaft 16. Analogously, the second piston 11 is actuated by a second rocker arm 13 and a second cam 15 on a second camshaft 17. The first and the second rocker arms 12, 13 are mounted on a common axis 18. The first rocker arm 12 has an integrally formed driver 19 which actuates the second rocker arm 13 when the first rocker arm 12 is not actuated.

Weiters ist der Arbeitsraum 7 und die damit zusammenhängenden Zylinderräume 8, 9 über eine Verbindungsleitung 20 mit einem Schaltventil 21 verbunden. In der in Fig. 1 dargestellten Stellung wird die Verbindungsleitung 20 über eine Versorgungsleitung 22, in der ein Rückschlagventil 23 vorgesehen ist, mit Motoröl aus dem Motorölkreislauf versorgt. Alternativ dazu ist jedoch auch eine Fremdölversorgung möglich. Durch Umschaltung des Schaltventils 21 kann der Arbeitsraum 7 mit dem Leckölsystem 24 verbunden werden, wodurch die Ventilbetätigung verhindert wird und eine Ventilabschaltung erreicht wird.Furthermore, the working space 7 and the associated cylinder spaces 8, 9 are connected to a switching valve 21 via a connecting line 20. In the position shown in FIG. 1, the connecting line 20 is supplied with engine oil from the engine oil circuit via a supply line 22 in which a check valve 23 is provided. As an alternative, however, a foreign oil supply is also possible possible. By switching the switching valve 21, the working space 7 can be connected to the leakage oil system 24, whereby the valve actuation is prevented and valve shutdown is achieved.

In dem Diagramm von Fig. 3 wird die Variabilität des erfindungsgemäßen Ventiltriebs anhand eines Diagramms dargestellt. Über dem Kurbelwinkel KW ist der Ventilhub h in beliebigen Einheiten aufgetragen. Mit 30 ist ein erster Kurvenabschnitt bezeichnet, der einer frühen Öffnung des Gaswechselventils 1 entspricht. Je nach Festsetzung des Schließzeitpunktes setzt sich der Kurvenabschnitt 30 in den Kurvenabschnitten 31, 32 oder 33 fort, wobei 31 einem sehr frühen Schließen, 32 einem mittleren Schließen und 33 einem späten Schließen entspricht. Es ist ersichtlich, dass bei frühem Schließen gemäß Kurve 31 der maximale Ventilhub h nicht erreicht wird, da die Schließbewegung bereits beginnt, bevor die Öffnungsbewegung vollendet ist. In analoger Weise sind mit unterbrochenen Linien weitere Kurven 40, 41, 42 und 43 eingetragen, die den Kurven 30, 31, 32 und 33 entsprechen, wobei jedoch ein späterer Ventilöffnungszeitpunkt gegeben ist. Die Länge der Ventilöffnung und der Hub entsprechend den Kurven 41, 42 und 43 sind identisch denen im Fall der Kurven 31, 32 bzw. 33.In the diagram of FIG. 3, the variability of the valve train according to the invention is shown using a diagram. The valve stroke h is plotted in arbitrary units over the crank angle KW. 30 designates a first curve section, which corresponds to an early opening of the gas exchange valve 1. Depending on the setting of the closing time, the curve section 30 continues in the curve sections 31, 32 or 33, with 31 corresponding to a very early closing, 32 a medium closing and 33 a late closing. It can be seen that with early closing according to curve 31, the maximum valve lift h is not reached, since the closing movement begins before the opening movement is completed. In an analogous manner, further curves 40, 41, 42 and 43 are entered with broken lines, which correspond to curves 30, 31, 32 and 33, but with a later valve opening time. The length of the valve opening and the stroke corresponding to curves 41, 42 and 43 are identical to those in the case of curves 31, 32 and 33, respectively.

In Fig. 4 ist in einem Diagramm der Zusammenhang zwischen der Stellung der Nocken 14, 15 und der Ventilöffnung dargestellt. Die Kurve 51 stellt dabei die Erhebung des ersten Nockens 14 dar, die zwischen n0, dem Grundkreis, und n1, der Nockenerhebung, wechselt. Analog dazu stellt die Kurve 52 die Situation am zweiten Nocken 15 dar, die zwischen der Grundstellung m0 und der erhobenen Stellung m1 wechselt. Zu einem Zeitpunkt t0, der 0° Kurbelwinkel entspricht, ist der erste Nocken 14 in der erhobenen Stellung n1 und der zweite Nocken 15 in der Grundstellung m0. Dementsprechend ist das Gaswechselventil 1 in seiner geschlossenen Stellung.4 shows the relationship between the position of the cams 14, 15 and the valve opening in a diagram. The curve 51 represents the elevation of the first cam 14, which alternates between n 0 , the base circle, and n 1 , the cam elevation. Analogously, the curve 52 represents the situation on the second cam 15, which changes between the basic position m 0 and the raised position m 1 . At a time t 0 , which corresponds to a crank angle of 0 °, the first cam 14 is in the raised position n 1 and the second cam 15 is in the basic position m 0 . Accordingly, the gas exchange valve 1 is in its closed position.

Zum Zeitpunkt t1 beginnt am zweiten Nocken 15 die ansteigende Flanke, die sich bis zum Zeitpunkt t2 fortsetzt, in der der zweite Nocken 15 die erhobene Stellung m1 erreicht hat. Dieser Zeitabschnitt zwischen t1 und t2 entspricht der Öffnungsbewegung des Gaswechselventils 1. Bis zum Zeitpunkt t3 bleiben beide Nocken 14, 15 in der erhobenen Stellung n1, m1, und das Gaswechselventil 1 bleibt vollständig geöffnet. Zwischen den Zeitpunkten t3 und t4 sinkt der erste Nocken 14 auf seinen Grundkreis bei n0 ab, und dementsprechend schließt das Gaswechselventil 1 und ist ab dem Zeitpunkt t4 vollständig geschlossen. Zu einem beliebigen Zeitpunkt t5, der aber jedenfalls nach dem spätest möglichen Zeitpunkt t4 liegen muss, beginnt die absteigende Flanke des zweiten Nockens 15, wie aus der Kurve 52 ersichtlich ist. Da jedoch der Mitnehmer 19 des ersten Kipphebels 12 den zweiten Kipphebel 13 niederhält, hebt dieser vom zweiten Nocken 15 ab, so dass sich eine fiktive Nockenkurve 53 ergibt, die mit strichpunktierten Linien dargestellt ist. Der Zeitpunkt t6 entspricht dem Erreichen des Grundkreises des zweiten Nockens 15, was jedoch für das System bedeutungslos ist. Erst zu einem Zeitpunkt t7 beginnt die ansteigende Flanke des ersten Nockens 14 mit einer entsprechenden Bewegung des ersten Kipphebels 12, wodurch der Mitnehmer 19 den zweiten Kipphebel 13 entsprechend freigibt, bis dieser letztendlich wieder auf dem zweiten Nocken 15 aufsitzt. Im Zeitpunkt t8, der 720° Kurbelwinkel entspricht, ist diese Bewegung zu Ende und es beginnt ein neues Arbeitsspiel bei t0.At time t 1 , the rising edge begins at second cam 15, which continues until time t 2 , in which second cam 15 has reached the raised position m 1 . This time period between t 1 and t 2 corresponds to the opening movement of the gas exchange valve 1. Up to the time t 3 , both cams 14, 15 remain in the raised position n 1 , m 1 , and the gas exchange valve 1 remains completely open. Between times t 3 and t 4 , the first cam 14 sinks to its base circle at n 0 , and accordingly the gas exchange valve 1 closes and is completely closed from time t 4 . The descending flank of the second cam 15 begins at an arbitrary point in time t 5 , which in any case must be after the latest possible point in time t 4 , as can be seen from curve 52. However, since the driver 19 of the first rocker arm 12 holds down the second rocker arm 13, it lifts off the second cam 15, so that a fictitious cam curve 53 results, which is shown with dash-dotted lines is shown. The time t 6 corresponds to the reaching of the base circle of the second cam 15, but this is meaningless for the system. Only at a point in time t 7 does the rising flank of the first cam 14 begin with a corresponding movement of the first rocker arm 12, as a result of which the driver 19 accordingly releases the second rocker arm 13 until it finally rests on the second cam 15. At time t 8 , which corresponds to 720 ° crank angle, this movement has ended and a new work cycle begins at t 0 .

Aus Fig. 4 ist ersichtlich, dass der zweite Nocken 15 die Öffnungsbewegung des Gaswechselventils 1 veranlasst, wogegen der erste Nocken 14 die Schließbewegung bewirkt.4 that the second cam 15 initiates the opening movement of the gas exchange valve 1, whereas the first cam 14 effects the closing movement.

Durch die vorliegende Erfindung ist es in einfacher Weise möglich, die Ventilsteuerzeiten mit großen Freiheitsgraden festzulegen.The present invention makes it possible in a simple manner to determine the valve timing with large degrees of freedom.

Claims (11)

  1. An internal combustion engine with at least one cylinder and with at least one charge changing valve (1) that is controlled by a first camshaft (16) through a first cam (14) and by a second camshaft (17) through a second cam (15), at least one camshaft (16, 17) for varying the valve timing of the charge changing valve (1) being configured such that the phasing thereof is adjustable, the first cam (14) acting on a first hydraulic member (10) and the second cam (15) acting on a second hydraulic member (11) with both hydraulic members (10, 11) acting together on a third hydraulic member (5) that actuates the charge changing valve (1), characterized in that there is provided a lever mechanism that makes certain that the charge changing valve (1) will not open until both the first cam (14) and the second cam (15) are acting on the respective one of the hydraulic members (10, 11).
  2. The internal combustion engine according to claim 1, characterized in that the first cam (14) acts on the first hydraulic member (10) by use of a first rocker arm (12).
  3. The internal combustion engine according to one of the claims 1 or 2, characterized in that the second cam (15) acts on the second hydraulic member (11) by use of a second rocker arm (13).
  4. The internal combustion engine according to claim 2 and 3, characterized in that one common axis (18) provides bearing support for both the first rocker arm (12) and the second rocker arm (13).
  5. The internal combustion engine according to claim 2 and 3 or 4, characterized in that one of the rocker arms (12) is comprised of a preferably adjustable driver (19) for driving the other rocker arm (13) so that the latter is actuated when the first is not.
  6. The internal combustion engine according to one of the claims 1 through 5, characterized in that there is provided a pilot valve (21) that is configured to prevent the charge changing valve (1) from being actuated.
  7. The internal combustion engine according to one of the claims 1 through 6, characterized in that the hydraulic members (10, 11) are configured as hydraulic cylinders.
  8. The internal combustion engine according to one of the claims 1 through 7, characterized in that the charge changing valve (1), which is controlled by the first camshaft (16) and by the second camshaft (17), is an intake valve and that an exhaust valve is controlled by the first camshaft (16).
  9. The internal combustion engine according to one of the claims 1 through 8, characterized in that the first camshaft (16) and the second camshaft (17) are configured such that their phasing is adjustable independently of each other.
  10. The internal combustion engine according to one of the claims 1 through 9, characterized in that the third hydraulic member (5) acts on a valve bridge for actuating a plurality of charge changing valves (1) of the same type.
  11. The internal combustion engine according to one of the claims 1 through 10, characterized in that the hydraulic system comprising the hydraulic members (5; 10, 11) comprises a valve clearance compensation device.
EP02450145A 2002-06-28 2002-06-28 Internal combustion engine Expired - Lifetime EP1375843B1 (en)

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DE50200400T DE50200400D1 (en) 2002-06-28 2002-06-28 Internal combustion engine
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Applications Claiming Priority (1)

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EP02450145A EP1375843B1 (en) 2002-06-28 2002-06-28 Internal combustion engine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE355445T1 (en) * 2004-01-16 2006-03-15 Fiat Ricerche INTERNAL COMBUSTION ENGINE WITH A SINGLE OVERHEAD CAMSHAFT FOR MECHANICAL CONTROL OF EXHAUST VALVES AND ELECTROHYDRAULIC CONTROL OF INLET VALVES
AT500600B1 (en) * 2004-07-20 2007-09-15 Avl List Gmbh Internal combustion engine, has gas exchange valves controlled by two cams provided on respective camshafts, which have adjustable phase position to modify control time of valves, and rocker levers supported on common axle actuate valves
DE112005001390A5 (en) 2004-06-24 2007-05-10 Avl List Gmbh Internal combustion engine
KR101272942B1 (en) 2011-09-30 2013-06-11 현대자동차주식회사 Variable valve system
FR2986558B1 (en) * 2012-02-02 2014-03-07 Melchior Jean F DEVICE FOR VARIABLY CONTROLLING AT LEAST ONE VALVE, FOR EXAMPLE FOR AN ALTERNATIVE ENGINE
EP3184761B1 (en) 2015-12-24 2018-04-18 C.R.F. Società Consortile per Azioni System for variable actuation of a valve of an internal-combustion engine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2480854A1 (en) * 1980-04-22 1981-10-23 Renault Hydraulic valve control for IC engine - has oil filled chamber with two cam operated pistons controlling valve piston
US4716863A (en) * 1985-11-15 1988-01-05 Pruzan Daniel A Internal combustion engine valve actuation system
US4771742A (en) 1986-02-19 1988-09-20 Clemson University Method for continuous camlobe phasing
GB9001793D0 (en) * 1990-01-26 1990-03-28 Baker David J Multiple cam mechanism
DE4018586A1 (en) * 1990-06-09 1991-12-12 Audi Ag IC-engine with twin camshaft - has rocker arms mounted on pin aligned parallel to camshafts
DE4236600C2 (en) * 1992-10-29 1999-03-11 Audi Ag Valve actuation mechanism for a multi-cylinder internal combustion engine
DE19745761A1 (en) 1997-10-16 1999-04-22 Daimler Chrysler Ag Variable valve control for reciprocating piston internal combustion engines
AU2002225082A1 (en) * 2000-12-15 2002-06-24 Jean Frederic Melchior Variable timing device for reciprocating engines, engines comprising same and distribution and turbocharging method

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