EP2716882B1 - Mechanically controllable valve drive for a reciprocating piston engine - Google Patents

Mechanically controllable valve drive for a reciprocating piston engine Download PDF

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Publication number
EP2716882B1
EP2716882B1 EP13183705.6A EP13183705A EP2716882B1 EP 2716882 B1 EP2716882 B1 EP 2716882B1 EP 13183705 A EP13183705 A EP 13183705A EP 2716882 B1 EP2716882 B1 EP 2716882B1
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EP
European Patent Office
Prior art keywords
valve
lift
roller
region
gas exchange
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Not-in-force
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EP13183705.6A
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German (de)
French (fr)
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EP2716882A1 (en
Inventor
Prof.-Dr. Rudolf Flierl
Daniel Hosse
Frederic LAUER
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Kolbenschmidt Pierburg Innovations GmbH
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Kolbenschmidt Pierburg Innovations GmbH
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    • 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
    • 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
    • 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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • 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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type

Definitions

  • the invention relates to a mechanically controllable valve drive for a reciprocating engine, in particular an internal combustion engine of a motor vehicle, for the adjustment of gas exchange valves.
  • the mechanically controllable valve train consists of a cam arrangement, with a camshaft and at least one cam per gas exchange valve.
  • the valve train consists of a Ventilhubverstellan extract, which performs an adjustment of the valve between a zero stroke and a maximum stroke and substantially comprises a VentilhubverstellISS having at least one intermediate lever with a working curve, wherein the working curve has different curve areas.
  • the mechanically controllable valvetrain has a finger follower arrangement with which the working cam is operatively connected, providing means for providing a valve lift range such that the maximum lift valve is open for a cam torsion angle ⁇ with a flattened, in particular constant, valve lift height having a working curve with a Ventilhubstillstandsabêt, the working curve seen in the opening direction of the gas exchange valve has a zero stroke, an adjustment, and the Ventilhubstillstandsabêt.
  • Such mechanically controllable valve trains are well known from the prior art in the field of internal combustion engines. They serve in particular to adapt the combustion process to the respective load requirements by means of the valve lift height and valve opening duration, and thus the degree of filling of the cylinders of the internal combustion engine Accordingly, to ensure the most efficient and therefore low-emission combustion.
  • certain load ranges in particular the partial load range, to switch off a certain number of cylinders completely in order, for example, to operate the internal combustion engine with only two cylinders in a four-cylinder internal combustion engine.
  • the gas exchange valve is operated in the zero stroke range, which also means that the valve acceleration in this area is equal to zero.
  • valve train thus formed is thus highly dependent on the maximum achievable valve lift in terms of the filling volume.
  • Particularly large valve lifts here have the disadvantage that they require a large space for adjustment, increase the risk of piston collision, or arise higher frictional forces in an opening against the return spring of the gas exchange valve.
  • From the DE 196 29 349 A1 for this it is known, in addition to a zero stroke section, to also see a valve-lift stand section, which ensures greater variability with regard to the filling volume.
  • such a construction of a valve train is very expensive to install and manufacture and therefore expensive. In addition, this construction has very great disadvantages in terms of the effect of frictional forces.
  • DE 10 2004 009 389 on the other hand, a simple valve actuator to be provided is known which, due to its construction, causes an improved force flow.
  • the invention is therefore based on the object, a mechanically controllable fully variable valve train for a reciprocating engine in such a way that, inter alia, the disadvantages described above are avoided and a Ventilhubstillstand is possible.
  • the intermediate lever on its first arm that is on the working contour opposite side has a first roller which is moved by the cam of the camshaft directly or indirectly in a slide track; that the intermediate lever has a second roller in its pivoting center, which rolls on a contour of the Ventilhubverstell till and that the intermediate lever on its second arm, ie the backdrop opposite side, the working curve, which cooperates with a third roller of the finger follower arrangement, wherein both the Nullhubabterrorism, as well as the Ventilhubstillstandsabterrorism describe part of a curved path around the axial center of the first roller, wherein the radius r 1 of the Ventilhubstillstandsabiteses is greater than the radius r 2 of the Nullhubabiteses.
  • valve-lift stand-still range is characterized in that the slope and thus the acceleration go to zero or are zero in the stated range.
  • This arrangement allows the individual and variable adaptation of the valves and the then over a defined, longer cam torsion angle ⁇ predominantly constant holding the valve position achieved. Due to the special design of the valve lift range, the valve is in the maximum stroke of the mechanically controllable valve drive for a cam torsion angle ⁇ opened with flattened, in particular constant valve lift.
  • the adjustment of the intermediate lever that is, the change in the position of the pivot center of the intermediate lever with respect to the Ventilhubverstell Rhein, the valve lift or the opening time adjusted.
  • the drag lever assembly in turn is in operative connection with a gas exchange valve.
  • the arrangement described here is characterized by a compact design with simple adjustment of the valves.
  • the slide track describes a curved path around the center of the third roller of the finger follower arrangement.
  • the angle of rotation ⁇ of the camshaft in the region of the valve lift stand has a value between 30 ° and 150 °.
  • the acceleration curve in the region of the valve lift position preferably exhibits an acceleration of 0 mm / rad 2 for a camshaft twist angle range between 30 ° and 150 °.
  • the gas exchange valve actuating device has at least one hydraulic actuator.
  • the gas exchange valve can be designed both as an inlet and outlet valve.
  • an internal exhaust gas recirculation is readily possible because there is a high driving pressure difference between the exhaust gas side and the cylinder suction side due to the suction side throttling.
  • At least one gas exchange valve is designed as an outlet valve in the region of the gas exchange valve actuating device.
  • At least one gas inlet valve can be controlled by a variable valve drive.
  • the intermediate lever is supported with a circular contour on the Ventilhubverstell Surprise, said contour can also be supported on a sliding or roller bearing roller.
  • variable lift valve train is mechanically more stable, i. Among other things vibration less prone and there are reduced acceleration and vibration forces.
  • the speed of the engine and also the spring element are dimensioned smaller, which also in conjunction with the reduced acceleration forces of the intermediate lever, significantly higher speeds can be achieved.
  • a higher engine efficiency may be derived as a positive effect from the reduction of internal friction.
  • FIG. 1 A preferred embodiment of a mechanically controllable valve drive 10 shows FIG. 1 ,
  • the mechanically controllable valve drive 10 for a reciprocating engine essentially consists of an intermediate lever 28, which is movably mounted in a slide track 62 of a link 56, which is arranged stationarily in a cylinder head, not shown.
  • the link shape is determined by a circular arc which extends around the center of the first roller 52.
  • a camshaft 14 is arranged, which can be moved directly or indirectly with a first cam 16 and thereby drives the gas exchange valve 18.
  • the camshaft 14 also has a second cam 19 to allow a second stroke of the valve lift curve of the gas outlet valve 18.
  • the gas exchange valve 18 is cyclically opened and closed, provided there is an operative connection between the working curve 30 and a third roller 64 of a finger follower arrangement 32.
  • intermediate levers are also covered by the invention.
  • two intermediate levers can be arranged on an axle with a roller, this roller is then guided in a backdrop. In this context, on the DE 10 140 635 A1 to get expelled.
  • a Ventilhubverstell Rhein 24 Coaxial with the first roller 52 and approximately midway between the slide track 62 and the working curve 30 is a Ventilhubverstell noticed 24 arranged with a second roller 54.
  • the valve lift adjusting device 24 With the valve lift adjusting device 24, the absolute stroke of the gas exchange valve 18 and the opening time of a valve 22 are set.
  • the intermediate lever 28 has a working curve 30 with a zero stroke section 40, a Verstellhubabites 42 and a Ventilhubstillstandsabites 34.
  • the intermediate lever 28 is connected via a third roller 64 with a finger lever assembly 32 in operative connection.
  • a finger lever assembly 32 is mounted on the one hand on a lash adjuster, preferably a hydraulic valve lash adjuster and acts with the gas exchange valve 18.
  • the gas exchange valve 18 and the lash adjuster are mounted in the cylinder head, not shown here.
  • FIG. 2 shows a section of the mechanically controllable valve train 10.
  • the intermediate lever 28 is shown with the working curve 30 according to the invention.
  • the working curve 30 has in the opening direction seen the zero stroke section 40, the adjustment section 42 and the Ventilhubstillstandsabrough 34.
  • the individual areas are interconnected by transition radii and connected to each other over the entire working curve area 30.
  • the acceleration behavior of the valve 22 of the internal combustion engine is also influenced by the various regions of the working curve 30.
  • the region-wise constant valve lift also defines the acceleration at defined camshaft twist angles ⁇ to almost zero.
  • FIG. 3 is a diagram in which a valve lift and the valve acceleration of the gas exhaust valve 18 are off.
  • FIG. 2 via a cam torsion angle ⁇ of an internal combustion engine are shown.
  • the dotted line shows the course of the stroke of the valve 22 and the dashed line shows the course of the acceleration of the valve 22.
  • valve acceleration curve of the acceleration waveform with the valve lift stand area 35 shows a range of acceleration of 0 mm / rad 2 . This ensures that a large filling volume is ensured in comparison with a conventional, lower maximum stroke 44.
  • the Ventilhubstillstand Society 35 In the region of the valve acceleration equal to zero and the constant Ventilhubweg at a Nockenvertextwinkel ⁇ of about 100 ° is the Ventilhubstillstand Scheme 35. This flattened, in particular constant Ventilhubstillstands Scheme 35 extends over a Nockenvertextwinkel ⁇ of about 40 °, but can also have a larger Range, such as 150 °, extend. At this time, the valve 22 is not opened further. By the standstill, the mechanical complexity and the friction caused by the spring force is reduced and saves additional space.

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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 einen mechanisch steuerbaren Ventiltrieb für eine Hubkolbenmaschine, insbesondere eine Brennkraftmaschine eines Kraftfahrzeuges, zur Verstellung von Gaswechselventilen. Der mechanisch steuerbare Ventiltrieb besteht aus einer Nockenanordnung, mit einer Nockenwelle und mindestens einem Nocken pro Gaswechselventil. Des Weiteren besteht der Ventiltrieb aus einer Ventilhubverstellanordnung, die eine Verstellung des Ventils zwischen einem Nullhub und einem Maximalhub vornimmt und im Wesentlichen eine Ventilhubverstelleinrichtung aufweist, die mindestens einen Zwischenhebel mit einer Arbeitskurve aufweist, wobei die Arbeitskurve verschiedene Kurvenbereiche besitzt. Überdies weist der mechanisch steuerbare Ventiltrieb eine Schlepphebelanordnung auf, mit der die Arbeitskurve in Wirkverbindung steht wobei Mittel vorgesehen sind, die einen Ventilhubstillstandsbereich bereitstellen, derart, dass das Ventil mit Maximalhub für einen Nockenverdrehwinkel ω mit abgeflachter, insbesondere konstanter Ventilhubhöhe geöffnet ist, wobei die Mittel eine Arbeitskurve mit einem Ventilhubstillstandsabschnitt aufweisen, wobei die Arbeitskurve in Öffnungsrichtung des Gaswechselventils gesehen einen Nullhubabschnitt, einen Verstellabschnitt, sowie den Ventilhubstillstandsabschnitt besitzt.The invention relates to a mechanically controllable valve drive for a reciprocating engine, in particular an internal combustion engine of a motor vehicle, for the adjustment of gas exchange valves. The mechanically controllable valve train consists of a cam arrangement, with a camshaft and at least one cam per gas exchange valve. Furthermore, the valve train consists of a Ventilhubverstellanordnung, which performs an adjustment of the valve between a zero stroke and a maximum stroke and substantially comprises a Ventilhubverstelleinrichtung having at least one intermediate lever with a working curve, wherein the working curve has different curve areas. Moreover, the mechanically controllable valvetrain has a finger follower arrangement with which the working cam is operatively connected, providing means for providing a valve lift range such that the maximum lift valve is open for a cam torsion angle ω with a flattened, in particular constant, valve lift height having a working curve with a Ventilhubstillstandsabschnitt, the working curve seen in the opening direction of the gas exchange valve has a zero stroke, an adjustment, and the Ventilhubstillstandsabschnitt.

Derartige mechanisch steuerbare Ventiltriebe sind aus dem Stand der Technik im Bereich der Brennkraftmaschinen hinlänglich bekannt. Sie dienen insbesondere dazu, mittels der Ventilhubhöhe und Ventilöffnungsdauer, und damit dem Füllgrad der Zylinder der Brennkraftmaschine, den Verbrennungsprozess den jeweiligen Lastanforderungen anzupassen und dementsprechend für eine möglichst effiziente und damit auch schadstoffarme Verbrennung zu sorgen. Darüber hinaus ist es bekannt, in bestimmten Lastbereichen, insbesondere dem Teillastbereich, eine gewisse Anzahl von Zylindern komplett abzuschalten, um beispielsweise bei einer Vierzylinder-Brennkraftmaschine die Brennkraftmaschine lediglich mit zwei Zylindern zu betreiben. Hier wird das Gaswechselventil im Nullhubbereich betrieben, was gleichzeitig bedeutet, dass die Ventilbeschleunigung in diesem Bereich gleich Null ist. An diesen Nullhubbereich schließt sich ein Verstellbereich an, der an einem bestimmten Verdrehwinkelpunkt einen Maximalhub des Gaswechselventils bewirkt. Das Integral unter der gesamten Ventilhubkurve bestimmt somit das Füllvolumen bei einem Gaswechsel-Einlassventil, beziehungsweise Abgasausstoßvolumen bei einem Gaswechsel-Auslassventil.Such mechanically controllable valve trains are well known from the prior art in the field of internal combustion engines. They serve in particular to adapt the combustion process to the respective load requirements by means of the valve lift height and valve opening duration, and thus the degree of filling of the cylinders of the internal combustion engine Accordingly, to ensure the most efficient and therefore low-emission combustion. In addition, it is known in certain load ranges, in particular the partial load range, to switch off a certain number of cylinders completely in order, for example, to operate the internal combustion engine with only two cylinders in a four-cylinder internal combustion engine. Here, the gas exchange valve is operated in the zero stroke range, which also means that the valve acceleration in this area is equal to zero. At this zero stroke adjoins an adjustment, which causes a maximum angle of the gas exchange valve at a certain angle of rotation. The integral below the entire valve lift curve thus determines the filling volume in the case of a gas exchange inlet valve or exhaust gas emission volume in the case of a gas exchange outlet valve.

Ein derartig ausgebildeter Ventiltrieb ist also hinsichtlich des Befüllungsvolumens in starkem Maße abhängig vom maximal zu erreichenden Ventilhub. Besonders große Ventilhübe weisen hierbei den Nachteil auf, dass sie einen großen Bauraum zur Verstellmöglichkeit benötigen, die Gefahr einer Kolbenkollision erhöhen, beziehungsweise höhere Reibungskräfte bei einem Öffnen gegen die Rückstellfeder des Gaswechselventils entstehen. Aus der DE 196 29 349 A1 ist es hierzu bekannt, neben einem Nullhubabschnitt auch einen Ventilhubstillstandsabschnitt vor zu sehen, wodurch eine größere Variabilität hinsichtlich des Befüllungsvolumens gewährleistet ist. Eine derartige Konstruktion eines Ventiltriebes ist jedoch sehr aufwendig in der Montage und Fertigung und daher teuer. Zudem weist diese Konstruktion sehr große Nachteile hinsichtlich der Wirkung von Reibungskräften auf. Aus der De 10 2004 009 389 ist dahingegen ein einfacher her zu stellender Ventiltrieb bekannt, der durch seinen Aufbau einen verbesserten Kraftfluss bedingt.Such a valve train thus formed is thus highly dependent on the maximum achievable valve lift in terms of the filling volume. Particularly large valve lifts here have the disadvantage that they require a large space for adjustment, increase the risk of piston collision, or arise higher frictional forces in an opening against the return spring of the gas exchange valve. From the DE 196 29 349 A1 For this it is known, in addition to a zero stroke section, to also see a valve-lift stand section, which ensures greater variability with regard to the filling volume. However, such a construction of a valve train is very expensive to install and manufacture and therefore expensive. In addition, this construction has very great disadvantages in terms of the effect of frictional forces. From DE 10 2004 009 389, on the other hand, a simple valve actuator to be provided is known which, due to its construction, causes an improved force flow.

Der Erfindung liegt daher die Aufgabe zugrunde, einen mechanisch steuerbaren vollvariablen Ventiltrieb für eine Hubkolbenmaschine derart auszugestalten, dass unter anderem die oben beschriebenen Nachteile vermieden werden und ein Ventilhubstillstand ermöglicht wird.The invention is therefore based on the object, a mechanically controllable fully variable valve train for a reciprocating engine in such a way that, inter alia, the disadvantages described above are avoided and a Ventilhubstillstand is possible.

Die Aufgabe wird dadurch gelöst, dass der Zwischenhebel an seinem ersten Arm, d.h. an der der Arbeitskontur entgegengesetzter Seite eine erste Rolle aufweist, die durch den Nocken der Nockenwelle direkt oder indirekt in einer Kulissenbahn bewegt wird; dass der Zwischenhebel in seinem Schwenkzentrum eine zweite Rolle aufweist, die sich an einer Kontur der Ventilhubverstelleinrichtung abwälzt und dass der Zwischenhebel an seinem zweiten Arm, d.h. der Kulisse entgegengesetzten Seite, die Arbeitskurve aufweist, die mit einer dritten Rolle der Schlepphebelanordnung zusammenwirkt, wobei sowohl der Nullhubabschnitt, als auch der Ventilhubstillstandsabschnitt einen Teil einer Kurvenbahn um den Achsmittelpunkt der ersten Rolle beschreiben, wobei der Radius r1 des Ventilhubstillstandsabschnittes größer ist als der Radius r2 des Nullhubabschnittes.The object is achieved in that the intermediate lever on its first arm, that is on the working contour opposite side has a first roller which is moved by the cam of the camshaft directly or indirectly in a slide track; that the intermediate lever has a second roller in its pivoting center, which rolls on a contour of the Ventilhubverstelleinrichtung and that the intermediate lever on its second arm, ie the backdrop opposite side, the working curve, which cooperates with a third roller of the finger follower arrangement, wherein both the Nullhubabschnitt, as well as the Ventilhubstillstandsabschnitt describe part of a curved path around the axial center of the first roller, wherein the radius r 1 of the Ventilhubstillstandsabschnittes is greater than the radius r 2 of the Nullhubabschnittes.

Hierdurch ist es auf einfache Weise möglich, besonders schnelle Ventilhübe bei geringem Bauraum mit hohem Füllgrad durchzuführen. Ein derartiger Ventilhubstillstandsbereich zeichnet sich dadurch aus, dass die Steigung und damit die Beschleunigung gegen Null gehen oder im genannten Bereich Null sind. Diese Anordnung erlaubt das individuelle und variable Anpassen der Ventile und das daraufhin über einen definierten, längeren Nockenverdrehwinkel ω vorwiegend konstante Halten der erzielten Ventilstellung. Durch die spezielle Ausbildung des Ventilhubstillstandbereiches ist das Ventil im Maximalhub des mechanisch steuerbaren Ventiltriebes für einen Nockenverdrehwinkel ω mit abgeflachter, insbesondere konstanter Ventilhubhöhe geöffnet.As a result, it is possible in a simple manner to carry out particularly fast valve lifts with a small space with a high degree of filling. Such a valve-lift stand-still range is characterized in that the slope and thus the acceleration go to zero or are zero in the stated range. This arrangement allows the individual and variable adaptation of the valves and the then over a defined, longer cam torsion angle ω predominantly constant holding the valve position achieved. Due to the special design of the valve lift range, the valve is in the maximum stroke of the mechanically controllable valve drive for a cam torsion angle ω opened with flattened, in particular constant valve lift.

Hierbei wird durch die Verstellung des Zwischenhebels, das bedeutet die Veränderung der Position des Schwenkzentrums des Zwischenhebels in Bezug auf die Ventilhubverstelleinrichtung, die Ventilhubhöhe bzw. die Öffnungszeit angepasst. Die Schlepphebelanordnung steht wiederum mit einem Gaswechselventil in Wirkverbindung.Here, the adjustment of the intermediate lever, that is, the change in the position of the pivot center of the intermediate lever with respect to the Ventilhubverstelleinrichtung, the valve lift or the opening time adjusted. The drag lever assembly in turn is in operative connection with a gas exchange valve.

Die hier beschriebene Anordnung zeichnet sich durch eine kompakte Bauweise bei einfacher Verstellung der Ventile aus.The arrangement described here is characterized by a compact design with simple adjustment of the valves.

Vorzugsweise beschreibt die Kulissenbahn eine Kurvenbahn um den Mittelpunkt der dritten Rolle der Schlepphebelanordnung.Preferably, the slide track describes a curved path around the center of the third roller of the finger follower arrangement.

In einer bevorzugten Ausführungsform weist der Verdrehwinkel ω der Nockenwelle im Bereich des Ventilhubstillstandes einen Wert zwischen 30° und 150° auf. Zudem zeigt der Beschleunigungsverlauf im Bereich des Ventilhubstillstandes bei einem Nockenwellenverdrehwinkelbereich zwischen 30° und 150° vorzugsweise eine Beschleunigung von 0 mm/rad2 auf.In a preferred embodiment, the angle of rotation ω of the camshaft in the region of the valve lift stand has a value between 30 ° and 150 °. In addition, the acceleration curve in the region of the valve lift position preferably exhibits an acceleration of 0 mm / rad 2 for a camshaft twist angle range between 30 ° and 150 °.

Des Weiteren weist die Gaswechselventilbetätigungsvorrichtung wenigstens einen hydraulischen Aktuator auf.Furthermore, the gas exchange valve actuating device has at least one hydraulic actuator.

Das Gaswechselventil kann sowohl als Einlass- als auch als Auslassventil ausgeführt sein. So ist insbesondere beim Ottomotor mit derartigen Ventiltriebanordnungen eine interne Abgasrückführung ohne weiteres möglich, da es aufgrund der saugseitigen Drosselung eine hohe treibende Druckdifferenz zwischen Abgasseite und Zylindersaugseite gibt.The gas exchange valve can be designed both as an inlet and outlet valve. Thus, in particular in the gasoline engine with such valve train arrangements, an internal exhaust gas recirculation is readily possible because there is a high driving pressure difference between the exhaust gas side and the cylinder suction side due to the suction side throttling.

In einer bevorzugten Ausführungsform ist im Bereich der Gaswechselventilbetätigungsvorrichtung mindestens ein Gaswechselventil als Auslassventil ausgeführt.In a preferred embodiment, at least one gas exchange valve is designed as an outlet valve in the region of the gas exchange valve actuating device.

In einer weiteren bevorzugten Ausführungsform ist mindestens ein Gaseinlassventil durch einen variablen Ventiltrieb ansteuerbar.In a further preferred embodiment, at least one gas inlet valve can be controlled by a variable valve drive.

Eine bevorzugte Weiterbildung ist darin zu sehen, dass sich der Zwischenhebel mit einer kreisförmigen Kontur an der Ventilhubverstelleinrichtung abstützt, wobei diese Kontur sich auch auf einer gleit- oder wälzgelagerten Rolle abstützen kann.A preferred development is to be seen in that the intermediate lever is supported with a circular contour on the Ventilhubverstelleinrichtung, said contour can also be supported on a sliding or roller bearing roller.

Durch die gesamte Vorrichtung sind die Reibungsverluste und der Bauteilverschleiß wesentlich verringert und die Lebensdauer des hubvariablen Ventiltriebes ist deutlich verlängert. Insgesamt ist der hubvariable Ventiltrieb mechanisch stabiler, d.h. unter anderem schwingungstechnisch weniger anfällig und es treten verringerte Beschleunigungs- und Schwingungskräfte auf. Als Folge hieraus kann zum einen durch die Reduktion der schwingungstechnischen Probleme die Drehzahl der Brennkraftmaschine problemlos erhöht werden und ferner das Federelement kleiner dimensioniert werden, wodurch auch in Verbindung mit den reduzierten Beschleunigungskräften des Zwischenhebels, deutlich höhere Drehzahlen erreichbar sind. Als positiver Effekt aus der Reduktion der inneren Reibung darf darüber hinaus eine höhere Motoreffizienz abgeleitet werden.Through the entire device, the friction losses and component wear are significantly reduced and the life of the variable stroke valve train is significantly extended. Overall, the variable lift valve train is mechanically more stable, i. Among other things vibration less prone and there are reduced acceleration and vibration forces. As a result, on the one hand can be easily increased by the reduction of vibration problems, the speed of the engine and also the spring element are dimensioned smaller, which also in conjunction with the reduced acceleration forces of the intermediate lever, significantly higher speeds can be achieved. In addition, a higher engine efficiency may be derived as a positive effect from the reduction of internal friction.

Die Erfindung wird nachfolgend anhand der Zeichnungen näher erläutert, hierin zeigen:

Figur 1
bevorzugte Ausführungsform der erfindungsgemäßen Vorrichtung für ein Gaswechselventil bei Maximalhub,
Figur 2
perspektivische Ansicht einer Ausführungsform des Zwischenhebels mit der erfindungsgemäßen Arbeitskurve, und
Figur 3
ein Diagramm, bei dem auf der Y-Achse der Ventilhub [mm] bzw. die Ventilbeschleunigung [rad/mm2] und auf der X-Achse der Nockenverdrehwinkel ω [°] dargestellt ist.
The invention will be explained in more detail below with reference to the drawings, in which:
FIG. 1
preferred embodiment of the device according to the invention for a gas exchange valve at maximum stroke,
FIG. 2
perspective view of an embodiment of the intermediate lever with the working curve according to the invention, and
FIG. 3
a diagram in which the valve lift [mm] or the valve acceleration [rad / mm 2 ] on the Y axis and the cam torsion angle ω [°] on the X axis is shown.

Der nachfolgend mechanische Ventiltrieb ist hinlänglich unter dem Namen "Univalve" bekannt. Hinsichtlich des Aufbaus und der Funktionsweise eines derartigen Ventiltriebes wird auf die EP 1 618 293 B1 verwiesen.The following mechanical valve train is well known under the name "Univalve". With regard to the structure and operation of such a valve train is on the EP 1 618 293 B1 directed.

Eine bevorzugte Ausführungsform eines mechanisch steuerbaren Ventiltriebes 10 zeigt Figur 1. Der mechanisch steuerbaren Ventiltrieb 10 für eine Hubkolbenmaschine besteht im Wesentlich aus einem Zwischenhebel 28, der schiebebeweglich in einer Kulissenbahn 62 einer Kulisse 56 gelagert ist, die ortsfest in einem nicht dargestellten Zylinderkopf angeordnet ist. Die Kulissenform ist dabei durch einen Kreisbogen bestimmt, der um Achsmittelpunkt der ersten Rolle 52 verläuft. Im Bereich dieser ersten Rolle 52 ist eine Nockenwelle 14 angeordnet, die mit einem ersten Nocken 16 direkt oder indirekt verschoben werden kann und dadurch das Gaswechselventil 18 antreibt. Um eine interne Abgasrückführung auf einfache und kostengünstige Weise zu ermöglichen, weist die Nockenwelle 14 darüber hinaus noch einen zweiten Nocken 19 auf, um einen Zweithub der Ventilerhebungskurve des Gasauslassventils 18 zu ermöglichen. Mit der Nockenwelle 14 wird das Gaswechselventil 18 zyklisch geöffnet und geschlossen, sofern eine Wirkverbindung zwischen der Arbeitskurve 30 und einer dritten Rolle 64 einer Schlepphebelanordnung 32 besteht. Es sind natürlich auch alternative Ausführungsformen von Zwischenhebeln durch die Erfindung erfasst. So können zwei Zwischenhebel auf einer Achse mit einer Rolle angeordnet sein, wobei diese Rolle dann in einer Kulisse geführt ist. In diesem Zusammenhang kann auf die DE 10 140 635 A1 verwiesen werden.A preferred embodiment of a mechanically controllable valve drive 10 shows FIG. 1 , The mechanically controllable valve drive 10 for a reciprocating engine essentially consists of an intermediate lever 28, which is movably mounted in a slide track 62 of a link 56, which is arranged stationarily in a cylinder head, not shown. The link shape is determined by a circular arc which extends around the center of the first roller 52. In the region of this first roller 52, a camshaft 14 is arranged, which can be moved directly or indirectly with a first cam 16 and thereby drives the gas exchange valve 18. In order to allow an internal exhaust gas recirculation in a simple and cost-effective manner, the camshaft 14 also has a second cam 19 to allow a second stroke of the valve lift curve of the gas outlet valve 18. With the camshaft 14, the gas exchange valve 18 is cyclically opened and closed, provided there is an operative connection between the working curve 30 and a third roller 64 of a finger follower arrangement 32. Of course, alternative embodiments of intermediate levers are also covered by the invention. Thus, two intermediate levers can be arranged on an axle with a roller, this roller is then guided in a backdrop. In this context, on the DE 10 140 635 A1 to get expelled.

Koaxial zur ersten Rolle 52 und in etwa mittig zwischen der Kulissenbahn 62 und der Arbeitskurve 30 ist eine Ventilhubverstelleinrichtung 24 mit einer zweiten Rolle 54 angeordnet. Mit der Ventilhubverstelleinrichtung 24 werden der Absoluthub des Gaswechselventils 18 sowie die Öffnungszeit eines Ventils 22 eingestellt.Coaxial with the first roller 52 and approximately midway between the slide track 62 and the working curve 30 is a Ventilhubverstelleinrichtung 24 arranged with a second roller 54. With the valve lift adjusting device 24, the absolute stroke of the gas exchange valve 18 and the opening time of a valve 22 are set.

Am gegenüberliegenden Ende zur Kulissenbahn 62 weist der Zwischenhebel 28 eine Arbeitskurve 30 mit einem Nullhubabschnitt 40, einem Verstellhubabschnitt 42 und einem Ventilhubstillstandsabschnitt 34 auf.At the opposite end to the slide track 62, the intermediate lever 28 has a working curve 30 with a zero stroke section 40, a Verstellhubabschnitt 42 and a Ventilhubstillstandsabschnitt 34.

Desweiteren steht der Zwischenhebel 28 über eine dritte Rolle 64 mit einer Schlepphebelanordnung 32 in Wirkverbindung. Über diese Wirkverbindung sind verschiedene Ventilhubpositionen des Gasauslassventils 18 ansteuerbar. Die Schlepphebelanordnung 32 ist einerseits auf einem Spielausgleichselement, vorzugsweise einem hydraulischen Ventilspielausgleichselement gelagert und wirkt mit dem Gaswechselventil 18. Das Gaswechselventil 18 und das Ventilspielausgleichselement sind in dem hier nicht dargestellten Zylinderkopf montiert.Furthermore, the intermediate lever 28 is connected via a third roller 64 with a finger lever assembly 32 in operative connection. About this operative connection different valve lift positions of the gas outlet valve 18 can be controlled. The finger follower assembly 32 is mounted on the one hand on a lash adjuster, preferably a hydraulic valve lash adjuster and acts with the gas exchange valve 18. The gas exchange valve 18 and the lash adjuster are mounted in the cylinder head, not shown here.

Befindet sich der Linienkontakt der dritten Rolle 64 auf der im Nullhubabschnitt 40 der Arbeitskurve 30, dann ist der Gaswechselventilhub 44 gleich Null, wird der Linienkontakt entlang der Öffnungsrichtung entlang des Verstellabschnittes 42 der Arbeitskurve 30 bis zum Ventilhubstillstandsabschnitt 34 verschoben, so vergrößert sich der Hub des Gaswechselventils 18 bis zu einem maximalen Wert. Erreicht der Linienkontakt dann den Bereich des Ventilhubstillstandabschnittes 34, wird der maximal erreichte Wert für einen definierten Nockenverdrehwinkel ω, hier ca. 40°, nahezu konstant gehalten.If the line contact of the third roller 64 is zero in the zero stroke section 40 of the working curve 30, then the Gaswechselventilhub 44 is zero, the line contact along the opening direction along the adjustment portion 42 of the working curve 30 is displaced to the Ventilhubstillstandsabschnitt 34 so increases the stroke of Gas exchange valve 18 up to a maximum value. If the line contact then reaches the area of the valve lift stand section 34, the maximum value achieved for a defined cam slip angle ω, here approximately 40 °, is kept almost constant.

Durch die Verwendung der Arbeitskurve 30 ist der Zwischenhebel 28 stets in Bewegung, so dass keine statische Flächenpressung in den Kontaktflächen auftreten und ständig ausreichende Schmierung der Kontaktflächen gewährleistet ist. Somit führt die erfindungsgemäße Ausgestaltung zu einer geringeren Reibung und zu weniger Verschleiß. Darüber hinaus sind die Zwischenhebelöffnungs- und Schließbewegungen durch die Verwendung der Ventilhubverstelleinrichtung 24 wesentlich reduziert, wodurch deutlich höhere Drehzahlen der Brennkraftmaschine möglich sind. Als weiterer Vorteil daraus ist die mögliche kleinere Dimensionierung des Federelementes anzuführen. Ferner sind Resonanzeffekte in dem Federelement durch die ständige Bewegung des Zwischenhebels 28 vermieden. Durch die Optimierung des Federelementes sind wiederum höhere Drehzahlen erreichbar, bei gleichzeitig minimierter Reibung und minimiertem Verschleiß.By using the working curve 30 of the intermediate lever 28 is always in motion, so that no static surface pressure in the contact surfaces occur and constantly adequate lubrication of the contact surfaces is guaranteed. Thus, the leads inventive design for a lower friction and less wear. In addition, the Zwischenhebelöffnungs- and closing movements are substantially reduced by the use of the Ventilhubverstelleinrichtung 24, whereby significantly higher speeds of the internal combustion engine are possible. Another advantage of this is the possible smaller dimensions of the spring element to cite. Furthermore, resonance effects in the spring element are avoided by the constant movement of the intermediate lever 28. By optimizing the spring element in turn higher speeds can be achieved, while minimizing friction and minimized wear.

Figur 2 zeigt einen Ausschnitt des mechanisch steuerbaren Ventiltriebes 10. In dieser Figur ist der Zwischenhebel 28 mit der erfindungsgemäßen Arbeitskurve 30 dargestellt. Die Arbeitskurve 30 weist dabei in Öffnungsrichtung gesehen den Nullhubabschnitt 40, den Verstellabschnitt 42 sowie den Ventilhubstillstandsabschnitt 34 auf. Durch diese Abfolge der Arbeitskurvenbereiche 30 wird die Öffnungscharakteristik des Gaswechselventils 18 festgelegt. Die einzelnen Bereiche sind durch Übergangsradien miteinander verbunden und über den gesamten Arbeitskurvenbereich 30 miteinander verbunden. FIG. 2 shows a section of the mechanically controllable valve train 10. In this figure, the intermediate lever 28 is shown with the working curve 30 according to the invention. The working curve 30 has in the opening direction seen the zero stroke section 40, the adjustment section 42 and the Ventilhubstillstandsabschnitt 34. By this sequence of the working curve areas 30, the opening characteristic of the gas exchange valve 18 is set. The individual areas are interconnected by transition radii and connected to each other over the entire working curve area 30.

Über die verschiedenen Bereiche der Arbeitskurve 30 wird neben der Hubhöhe und der Öffnungsdauer des Ventils 22 auch das Beschleunigungsverhalten des Ventils 22 der Verbrennungskraftmaschine beeinflusst. Durch den bereichsweise konstanten Ventilhub ist auch die Beschleunigung zu definierten Nockenwellenverdrehwinkeln ω zu nahezu Null definiert.In addition to the lifting height and the opening duration of the valve 22, the acceleration behavior of the valve 22 of the internal combustion engine is also influenced by the various regions of the working curve 30. The region-wise constant valve lift also defines the acceleration at defined camshaft twist angles ω to almost zero.

Figur 3 zeigt ein Diagramm, bei dem ein Ventilhub und die Ventilbeschleunigung des Gasauslassventils 18 aus Figur 2 über einen Nockenverdrehwinkel ω einer Brennkraftmaschine dargestellt sind. Die gepunktete Linie zeigt den Verlauf des Hubweges des Ventils 22 und die gestrichelte Linie zeigt den Verlauf der Beschleunigung des Ventils 22. Gegenüber der konventionellen Ventilhubkurve (siehe Strich-Punkt-Linie) des Gaswechsel-Auslassventils 18, d.h. ohne Ventilhubstillstandsbereich, weist die modifizierte Ventilhubwegkurve einen im Wesentlichen konstanten, unveränderten Hubbereich, dem Ventilhubstillstandsbereich 35, über einen Nockenverdrehwinkelbereich ω in einem Bereich zwischen 70° und 110° auf. Auch die Ventilbeschleunigungskurve des Beschleunigungsverlaufes mit dem Ventilhubstillstandsbereich 35 zeigt einen Bereich der Beschleunigung von 0 mm/rad2. Hierdurch wird erreicht, dass ein großes Füllvolumen bei gegenüber einem konventionellen, geringeren Maximalhub 44 gewährleistet ist. Im Bereich der Ventilbeschleunigung gleich Null und dem konstanten Ventilhubweg bei einem Nockenverdrehwinkel ω von rund 100° befindet sich der Ventilhubstillstandbereich 35. Dieser abgeflachte, insbesondere konstante Ventilhubstillstandsbereich 35 verläuft dabei über einen Nockenverdrehwinkel ω von ca. 40°, kann sich aber auch über einen größeren Bereich, wie z.B. 150°, erstrecken. Zu diesem Zeitpunkt wird das Ventil 22 nicht weiter geöffnet. Durch den Stillstand wird der mechanische Aufwand sowie die durch die Federkraft entstehende Reibung reduziert und zusätzlich Bauraum eingespart. Durch diese Anordnung werden weniger Anzeichen der Abnutzung im Vergleich zu anderen bekannten Anordnungen aufgezeigt. Es sollte deutlich sein, dass es natürlich auch möglich ist, den Ventilhubstillstandsbereich 35 sehr abgeflacht, also mit geringer Beschleunigung auszuführen. Wesentlich ist für die Erfindung, dass die Steigung im Bereich des Maximalhubes des Kurvenverlaufs sich in Richtung Null ändert. FIG. 3 FIG. 12 is a diagram in which a valve lift and the valve acceleration of the gas exhaust valve 18 are off. FIG FIG. 2 via a cam torsion angle ω of an internal combustion engine are shown. The dotted line shows the course of the stroke of the valve 22 and the dashed line shows the course of the acceleration of the valve 22. Compared with the conventional valve lift curve (see dash-dotted line) of the gas exchange exhaust valve 18, ie without Ventilhubstillstandsbereich, the modified Ventilhubwegkurve a substantially constant, unchanged stroke range, the Ventilhubstillstandsbereich 35, over a Nockenverdrehwinkelbereich ω in a range between 70 ° and 110 °. Also, the valve acceleration curve of the acceleration waveform with the valve lift stand area 35 shows a range of acceleration of 0 mm / rad 2 . This ensures that a large filling volume is ensured in comparison with a conventional, lower maximum stroke 44. In the region of the valve acceleration equal to zero and the constant Ventilhubweg at a Nockenverdrehwinkel ω of about 100 ° is the Ventilhubstillstandbereich 35. This flattened, in particular constant Ventilhubstillstandsbereich 35 extends over a Nockenverdrehwinkel ω of about 40 °, but can also have a larger Range, such as 150 °, extend. At this time, the valve 22 is not opened further. By the standstill, the mechanical complexity and the friction caused by the spring force is reduced and saves additional space. This arrangement shows less signs of wear compared to other known arrangements. It should be clear that, of course, it is also possible to flatten the valve-lift stand-off region 35 very much, that is, to carry out with low acceleration. It is essential for the invention that the slope in the region of the maximum stroke of the curve changes in the direction of zero.

Desweiteren ist in der Figur 3 ein zweiter Ventilhub (Second Event) des Gaswechsel-Auslassventils 18 dargestellt. Hierdurch kann in der Abgasauslassleitung vorhandenes Abgas durch das geöffnete Gaswechsel-Auslassventils 18 in den Zylinder zurückfließen, um so dem nachfolgenden Verbrennungsprozess zur Verfügung gestellt zu werden.Furthermore, in the FIG. 3 a second valve lift (Second Event) of the gas exchange outlet valve 18. As a result, exhaust gas present in the exhaust gas outlet line can flow back into the cylinder through the opened gas exchange exhaust valve 18 so as to be made available to the subsequent combustion process.

Eine Erhöhung des Maximalhubes 44 bei dem Second Event, eingestellt durch die Ventilhubverstellanordnung, wird zwar auch eine Erhöhung des Maximalhubes 44 beim Primärhub zur Folge haben, jedoch wird hierdurch die Erhöhung nicht so ausgeprägt stattfinden wie bei einem konventionellen Gaswechsel-Auslassventil 18.Although an increase of the maximum stroke 44 in the second event, set by the valve lift adjustment arrangement, will also result in an increase of the maximum stroke 44 during the primary stroke, however, the increase will not take place as pronounced as in a conventional gas exchange outlet valve 18.

Claims (8)

  1. Mechanically controllable valve drive (10) for a reciprocating piston machine, in particular an internal combustion engine of a motor vehicle, for the adjustment of gas exchange valves, comprising
    a cam arrangement (12) having a camshaft (14) and at least one cam (16) per gas exchange valve (18);
    a valve lift adjustment arrangement (20) performing an adjustment of the valve (22) between a zero lift (40) and a maximum lift (44) and substantially comprising a valve lift adjustment means (24) and an intermediate lever arrangement (26) which comprises at least one intermediate lever (28) having a work curve (30), the work curve (30) having different curve portions;
    and a rocker arm arrangement (32) with which the work curve is operatively connected, wherein
    means are provided that form a valve lift stop region (35) such that the valve (22), at its maximum lift (44), is opened over an angle of rotation ω of the camshaft (14) with a flattened, in particular constant valve lift height, wherein the means have a work curve (30) with a valve lift stop region (34), the work curve (30), seen in the opening direction of the gas exchange valve (18), comprises a zero lift region (40), an adjustment region (42) as well as the valve lift stop region (34),
    characterized in that
    the intermediate lever (28) has a first roller (52) at its first arm, which roller is moved directly or indirectly on the link path (62) of a link (56) by the cam (16) of the camshaft (14); the intermediate lever (28) has a second roller (56) at its centre of pivoting (66), which roller rolls on a contour of the valve lift adjustment means (24), and that the intermediate lever (28) has the work curve (30) at its second arm, the work curve cooperating with a third roller (64) of the rocker arm arrangement (32), wherein both the zero lift region (40) and the valve lift stop region (34) describe a part of a curved path around the fulcrum of the centre of the axis of the first roller (52), wherein the radius r1 of the valve lift stop region (34) is larger than the radius r2 of the zero lift region (40).
  2. Mechanically controllable valve drive (10) for a reciprocating piston machine of claim 1, characterized in that the link path (62) describes a curved path about the centre of the third roller (64) of the rocker arm arrangement (32).
  3. Mechanically controllable valve drive (10) for a reciprocating piston machine of claim 1 or 2, characterized in that, in the region of the valve lift stop (34), the angle of rotation ω of the camshaft (14) has a value between 30° and 150°.
  4. Mechanically controllable valve drive (10) for a reciprocating piston machine of one of the preceding claims, characterized in that the gas exchange valve (18) comprises at least one hydraulic actuator.
  5. Mechanically controllable valve drive (10) for a reciprocating piston machine of one of the preceding claims, characterized in that the at least one gas exchange valve (18) is designed as an outlet valve (22).
  6. Mechanically controllable valve drive (10) for a reciprocating piston machine of one of the preceding claims, characterized in that the camshaft (14) comprises a second cam (16) for the functionality of the second event.
  7. Internal combustion engine, in particular a diesel engine, with at least one working cylinder (60) having at least one inlet valve and one outlet valve (22), wherein at least one outlet valve (22) can be controlled by means of a valve drive (10) according to one of the preceding claims.
  8. Internal combustion engine of claim 10, characterized in that the at least one gas inlet valve (18) can be controlled by means of a variable valve drive.
EP13183705.6A 2012-10-08 2013-09-10 Mechanically controllable valve drive for a reciprocating piston engine Not-in-force EP2716882B1 (en)

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DE102012109538.8A DE102012109538A1 (en) 2012-10-08 2012-10-08 Mechanically controllable valve drive for a reciprocating engine

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DE102012109538A1 (en) 2014-04-10
US9279348B2 (en) 2016-03-08
US20140096730A1 (en) 2014-04-10

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