EP1636466B1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
EP1636466B1
EP1636466B1 EP04737352A EP04737352A EP1636466B1 EP 1636466 B1 EP1636466 B1 EP 1636466B1 EP 04737352 A EP04737352 A EP 04737352A EP 04737352 A EP04737352 A EP 04737352A EP 1636466 B1 EP1636466 B1 EP 1636466B1
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EP
European Patent Office
Prior art keywords
cam
internal combustion
combustion engine
camshaft
particular according
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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
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EP04737352A
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German (de)
French (fr)
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EP1636466A2 (en
Inventor
Johann Wagner
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AVL List GmbH
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AVL List GmbH
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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L1/34—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
    • 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
    • F01L13/0057—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 splittable or deformable 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
    • F01L2305/00—Valve arrangements comprising rollers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49293—Camshaft making

Definitions

  • the invention relates to an internal combustion engine having a variable valve drive device with at least one camshaft having at least one cam arrangement, which has a substantially radially with respect to the camshaft slidable cam and at least one, preferably two camshaft fixed base disks
  • a system for driving and controlling a cam for an internal combustion engine is known.
  • the cam is movable in the radial direction of the camshaft and includes a lift portion that moves fore and aft in the direction of the valve to be actuated, and includes means for engaging the cam with the camshaft and disengaging the cam from the camshaft in accordance with engine operating conditions.
  • the displacement of the cam takes place hydraulically.
  • a cam-type valve actuator for a lift valve which includes a cam having a rigid component radially adjustable between a retracted and an extended position, which is guided on the associated camshaft and associated with stops for limiting its exit movement.
  • the displacement of the cam is effected by a pressure medium supplied in a longitudinal bore of the camshaft.
  • variable valve trains have the disadvantage that complex control systems are required, and that for active actuation of the cam, the hydraulic actuation means must be provided at a relatively high pressure.
  • variable valve trains are usually suitable only for a certain type of operation, ie either for hydraulic, mechanical or electrical actuation.
  • the publication describes DE 102 17 695 A1 a starting method with changed timing of the intake valves to reduce the compression work during starting. Also the JP 1-1117840 A discloses the change in intake timing during the startup phase.
  • the object of the invention is to avoid these disadvantages and to propose a simple variable valve train device, which is suitable for external actuation with different actuating means, in particular to facilitate the starting process of an internal combustion engine.
  • the cam is actuated by an adjusting member arranged laterally of the camshaft.
  • the radially displaceable cam is thus controlled directly by the adjusting member arranged outside the camshaft.
  • the radially displaceable cam can be controlled in each case before or during the lifting phase of the adjusting member in the stroke position.
  • the adjusting member is formed by an actuating roller, which can be adjusted for example via an eccentric.
  • the radially displaceable cam can be supported on the camshaft via a resilient element and is pushed back after the lifting phase of this elastic element back into its initial position behind the base circle.
  • the cam is mounted on sliding surfaces on circular driving surfaces of the camshaft. Radius and angular position of the sliding surfaces are arranged so that no self-locking occurs at the beginning of the displacement of the cam.
  • the cam is designed in two parts, wherein viewed from a side view of the actuator, viewed in a side view substantially fork-shaped and encloses a cam lobe having second part, wherein the first and second part preferably via pins connected to each other.
  • the acted upon by the adjusting member first part encloses the cam elevation surface having a second part U-shaped and is connected thereto by two pins after being pushed onto the camshaft so that the first and second part of the cam form a cam unit.
  • the adjusting member has at least one engagement surface which cooperates with a corresponding corresponding counter surface of the first part of the cam.
  • the adjusting member has a substantially U-shaped cross-section with two legs forming the engagement surfaces, which are arranged at a distance from one another, which is greater than the width of the second part of the cam is very advantageous.
  • the adjusting member is effective only on the first part of the slidable cam and formed with a U-shaped cross section, in which the cam lobe of the second part can dip, so that no valve lift can take place in the working stroke phase of the internal combustion engine.
  • At least one base disc has a radial recess for mounting a pin, wherein preferably recesses of one base disc are offset from the recesses of the other base disc.
  • At least one base disc has a Rampenerhöhung, which forms a total cam together with the cam lobe of the second part of the cam.
  • the Rampenerhöhung the base circular discs form together with the cam lobe of the sliding cam from the total cam. Due to the Rampenerhöhungen the base circular disks and a defined base opening of the gas exchange valve can be generated.
  • the counter surface of the first part has a different shape from a cylindrical surface and defines a control surface, so that the Ventilhubkurve of the actuated lift valve from the shape of the mating surface of the first part and the shape of the cam lobe of the second Part of the cam composed, wherein preferably the counter surface and the cam lobe of the cam are formed so that the valve lift curve, in particular in the region of the transition between the base circle of the base discs for cam lobing steadily.
  • the fully variable valve actuation can be used in particular to facilitate the starting process in a diesel internal combustion engine.
  • the intake valve opening time is retarded and / or the intake closing time is advanced. This allows sufficient ignition conditions be achieved with lowered compression ratios.
  • the compression end temperature can be substantially increased if a repeated compression takes place with retractions of the cylinder contents in the intake manifold.
  • the shift of the opening time or the closing time can be up to 120 ° crank angle or more. Measurements have shown that a significant increase in the charge temperature in the region of top dead center of the compression of, for example, 70 ° to 120 °, depending on the speed can be achieved.
  • valve drive device 2 has two integral with the camshaft 1 base circular disks 3, a substantially radially displaceable on the camshaft 1 cam 4 and a directly acting on the cam 4 adjusting 5.
  • the cam 4 consists of two nested parts, one acted upon by the adjusting member 5 first part 6 and a cam lobe 7 having second part 8.
  • First and second part 6, 8 engage driving surfaces 9 of the camshaft 1, wherein the cam 4 in the area the driving surfaces have 9 sliding surfaces 10.
  • the first part 6 has a fork-shaped cross section, which comprises the second part 8, as seen from Fig. 2 is recognizable.
  • Diametrically with respect to the cam elevation 7, the first part 6 has a control cam 11, on which the adjusting member 5 acts on the cam 4.
  • the adjusting member 5 has in the embodiment, an actuating roller 12 with a in Substantially U-shaped cross section with two legs 23, which are formed by edges 13 of the actuating roller 12.
  • edges 13 act on engagement surfaces 21 on by the control surfaces 11 of the first part 6 of the cam 4 formed counter-surfaces 22 a.
  • the distance a of the edges 13 corresponds at least to the width b of the second part 8, so that no valve lift can take place in the working phase of the internal combustion engine.
  • the cam 4 is biased by an elastic member 14, wherein the elastic member 14, the cam 4 in the in Fig. 5 and Fig. 6 shown rest position presses, in which only the base circular disks 3 act on the valve actuator 15.
  • the first part 6 and the second part 8 of the cam 4 are based on each other and are connected to each other with pins 16. Via the elastic element 14, the cam 4 is pressed to a zero-stroke position, if there is no frictional connection via the feed roller 12.
  • radial mounting grooves 17 are provided in the base disks. The mounting grooves 17 are alternately arranged in the base disks 3 so as not to interrupt the contact of the valve actuator 15 to the base disks 3.
  • the actuating roller 12 is thus designed so that the cam lobe 7 dips into the free space 18 between the edges 13 when the internal combustion engine is in the working cycle. Outside the Zusüu fürsphase and the valve lift is no contact between the actuating roller 12 and the cam 4 is present, so that the valve actuator 15, which may be formed by a plunger, finger lever or rocker arm, in contact with the arranged on the camshaft 4 outside of the actuating roller 12 fixed base disks 3 is.
  • the driving surfaces 9, as well as the sliding surfaces 10, are arcuate. Your angular position and its radius is chosen so that the lowest possible adjustment possible, and that in any case, self-locking, especially at the beginning of the displacement of the cam 4, is avoided. Via a central bore 18 in the camshaft 1, pressure oil for lubricating the sliding surfaces 10 can be supplied without problems.
  • the base circular disks 3 may have a ramp region 19 which, together with the cam lobe 7 of the displaceable cam 4, forms the total cam.
  • the ramp region 19 defines a minimum stroke of the gas exchange valve, not shown, and allows a smooth transition from the base circle 20 of the base plate 3 on the cam elevation 7 and vice versa.
  • the shape of the valve lift curve is due to the interaction the control cam 11 defined with the cam lobe 7 of the displaceable cam 4 during the lifting phase. By appropriate shaping of the control cam 11 and the cam elevation 7, a uniform transition from the base circle 20 to the cam elevation 7 and vice versa is made possible.
  • Fig. 1 shows the valve drive device 2 to Verstellbeginn.
  • the actuating roller 12 is moved from the rest position indicated by reference numeral 12 'and indicated by dashed lines in the direction of the camshaft 1 according to the arrow P 1 , so that the edges 13 of the actuating roller 12 act on the control cam 11 of the first part 6 of the cam 4 and the cam 4 from the rest position against the force of the elastic element 14 in the FIG. 3 and FIG. 4 deflected illustrated stroke position.
  • the cam elevation 7 projects beyond the base circular disks 3 and thus acts on the valve actuator 15.
  • the camshaft 1 runs in the direction indicated by the arrow P 2 rotation.
  • the assembly of the first part 6 and the second part 8 on the camshaft 1 is carried out by pushing the same on the driving surfaces 9 from different sides. If the cam 4 against the force of the elastic element 14 in the in Fig. 3 Pressed stroke position shown, the pins 16 can be used by the radial grooves in the direction of the axis 1 a of the camshaft 1.
  • variable valve train 2 The advantage of the variable valve train 2 is that a large number of possible variations is possible by the external actuation by means of the adjusting member 5.
  • the adjusting member 5 can be operated pneumatically, hydraulically, electrically, electromagnetically, mechanically or in combination thereof.

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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 einer variablen Ventiltriebsvorrichtung mit zumindest einer Nockenwelle mit mindestens einer Nockenanordnung, welche einen im Wesentlichen radial bezüglich der Nockenwelle verschiebbaren Nocken und zumindest eine, vorzugsweise zwei nockenwellenfeste Grundkreisscheiben aufweistThe invention relates to an internal combustion engine having a variable valve drive device with at least one camshaft having at least one cam arrangement, which has a substantially radially with respect to the camshaft slidable cam and at least one, preferably two camshaft fixed base disks

Aus der DE 100 53 776 A1 ist ein System zum Antreiben und Steuern eines Nockens für einen Verbrennungsmotor bekannt. Der Nocken ist in der Radialrichtung der Nockenwelle bewegbar und umfasst einen Hubabschnitt, welcher sich vorwärts und rückwärts in der Richtung des zu betätigenden Ventils bewegt, wobei eine Vorrichtung vorgesehen ist, welche den Nocken mit der Nockenwelle in Eingriff bringt und den Nocken von der Nockenwelle löst, wobei dies in Übereinstimmung mit Motorbetriebszuständen erfolgt. Die Verschiebung des Nockens erfolgt dabei hydraulisch.From the DE 100 53 776 A1 For example, a system for driving and controlling a cam for an internal combustion engine is known. The cam is movable in the radial direction of the camshaft and includes a lift portion that moves fore and aft in the direction of the valve to be actuated, and includes means for engaging the cam with the camshaft and disengaging the cam from the camshaft in accordance with engine operating conditions. The displacement of the cam takes place hydraulically.

Aus der DE 42 22 477 A1 ist eine nockenbestückte Ventilbetätigung für ein Hubventil bekannt, welche einen Nocken mit einem in radialer Richtung zwischen einer eingefahrenen und einer ausgefahrenen Position verstellbaren starren Bauteil enthält, welcher an der zugehörigen Nockenwelle geführt ist und dem Anschläge zur Begrenzung seiner Ausfahrtbewegung zugeordnet sind. Die Verschiebung des Nockens erfolgt durch ein in einer Längsbohrung der Nockenwelle zugeführtes Druckmittel.From the DE 42 22 477 A1 For example, there is known a cam-type valve actuator for a lift valve which includes a cam having a rigid component radially adjustable between a retracted and an extended position, which is guided on the associated camshaft and associated with stops for limiting its exit movement. The displacement of the cam is effected by a pressure medium supplied in a longitudinal bore of the camshaft.

Hydraulisch betätigte variable Ventiltriebe haben den Nachteil, dass komplexe Regelungssysteme erforderlich sind, und dass zur aktiven Betätigung des Nockens das hydraulische Betätigungsmittel bei relativ hohem Druck bereitgestellt werden muss. Darüber hinaus eignen variable Ventiltriebe meistens nur für eine bestimmte Art von Betätigung, also entweder für hydraulische, mechanische oder für elektrische Betätigung.Hydraulically actuated variable valve trains have the disadvantage that complex control systems are required, and that for active actuation of the cam, the hydraulic actuation means must be provided at a relatively high pressure. In addition, variable valve trains are usually suitable only for a certain type of operation, ie either for hydraulic, mechanical or electrical actuation.

Aus den Veröffentlichungen DE 41 41 482 A1 , DE 37 37 824 A1 und DE 199 08 435 A1 ist es bekannt, beim Startvorgang Impulsaufladung durchzuführen bzw. den Einlassbeginn in der Startphase zu verzögern, um den Startvorgang zu vereinfachen.From the publications DE 41 41 482 A1 . DE 37 37 824 A1 and DE 199 08 435 A1 It is known to perform impulse charging during the starting process or to delay the beginning of the intake in the starting phase in order to simplify the starting process.

Weiters beschreibt die Veröffentlichung DE 102 17 695 A1 ein Startverfahren mit veränderten Steuerzeiten der Einlassventile zur Verringerung der Kompressionsarbeit während des Startens. Auch die JP 1-1117840 A offenbart die Veränderung der Einlasssteuerzeiten während der Startphase.Furthermore, the publication describes DE 102 17 695 A1 a starting method with changed timing of the intake valves to reduce the compression work during starting. Also the JP 1-1117840 A discloses the change in intake timing during the startup phase.

Aufgabe der Erfindung ist es, diese Nachteile zu vermeiden und eine einfache variable Ventiltriebseinrichtung vorzuschlagen, welche für externe Betätigung mit verschiedenen Betätigungsmitteln geeignet ist, insbesondere um den Startvorgang einer Brennkraftmaschine zu erleichtern.The object of the invention is to avoid these disadvantages and to propose a simple variable valve train device, which is suitable for external actuation with different actuating means, in particular to facilitate the starting process of an internal combustion engine.

Erfindungsgemäß wird dies dadurch erreicht, dass der Nocken durch ein seitlich der Nockenwelle angeordnetes Verstellglied ansteuerbar ist. Der radial verschiebbare Nocken wird somit direkt vom außerhalb der Nockenwelle angeordneten Verstellglied angesteuert. Dies hat den Vorteil, dass neben hydraulischen oder pneumatischen Verstellgliedern auch rein mechanische oder elektrische bzw. elektromagnetische Verstellglieder eingesetzt werden können. Die variable Ventiltriebsvorrichtung ist somit nicht auf eine bestimmte Art von Verstellgliedern eingeschränkt.According to the invention this is achieved in that the cam is actuated by an adjusting member arranged laterally of the camshaft. The radially displaceable cam is thus controlled directly by the adjusting member arranged outside the camshaft. This has the advantage that in addition to hydraulic or pneumatic adjustment also pure mechanical or electrical or electromagnetic adjustment can be used. The variable valve train device is thus not limited to a particular type of adjusters.

Der radial verschiebbare Nocken kann jeweils vor oder auch während der Hubphase vom Verstellglied in die Hubposition gesteuert werden. Vorzugsweise ist das Verstellglied durch eine Betätigungsrolle gebildet, welche beispielsweise über einen Exzenter verstellt werden kann.The radially displaceable cam can be controlled in each case before or during the lifting phase of the adjusting member in the stroke position. Preferably, the adjusting member is formed by an actuating roller, which can be adjusted for example via an eccentric.

Der radial verschiebbare Nocken kann sich über ein federndes Element an der Nockenwelle abstützen und wird nach der Hubphase von diesem elastischen Element wieder in seine Ausgangslage hinter den Grundkreis zurückgeschoben.The radially displaceable cam can be supported on the camshaft via a resilient element and is pushed back after the lifting phase of this elastic element back into its initial position behind the base circle.

Um eine klemmfreie Verschiebung es Nockens zu ermöglichen, ist es vorteilhaft, wenn der Nocken über Gleitflächen auf kreisförmigen Mitnahmeflächen der Nockenwelle gelagert ist. Radius und Winkellage der Gleitflächen sind so angeordnet, dass beim Beginn der Verschiebung des Nockens keine Selbsthemmung auftritt.In order to enable a jam-free displacement of the cam, it is advantageous if the cam is mounted on sliding surfaces on circular driving surfaces of the camshaft. Radius and angular position of the sliding surfaces are arranged so that no self-locking occurs at the beginning of the displacement of the cam.

In einer bevorzugten Ausführungsvariante der Erfindung ist vorgesehen, dass der Nocken zweiteilig ausgeführt ist, wobei ein vom Verstellglied beaufschlagter erster Teil in einer Seitenansicht betrachtet, im Wesentlichen gabelförmig ausgebildet ist und einen eine Nockenerhebung aufweisenden zweiten Teil umschließt, wobei erster und zweiter Teil vorzugsweise über Stifte miteinander verbunden sind. Der vom Verstellglied beaufschlagte erste Teil umschließt den eine Nockenerhebungsfläche aufweisenden zweiten Teil U-förmig und wird mit diesem durch zwei Stifte nach dem Aufschieben auf die Nockenwelle verbunden, so dass erster und zweiter Teil des Nockens eine Nockeneinheit bilden.In a preferred embodiment of the invention, it is provided that the cam is designed in two parts, wherein viewed from a side view of the actuator, viewed in a side view substantially fork-shaped and encloses a cam lobe having second part, wherein the first and second part preferably via pins connected to each other. The acted upon by the adjusting member first part encloses the cam elevation surface having a second part U-shaped and is connected thereto by two pins after being pushed onto the camshaft so that the first and second part of the cam form a cam unit.

Das Verstellglied weist zumindest eine Angriffsfläche auf, welche mit einer entsprechenden korrespondierenden Gegenfläche des ersten Teiles des Nockens zusammenwirkt.The adjusting member has at least one engagement surface which cooperates with a corresponding corresponding counter surface of the first part of the cam.

Sehr vorteilhaft ist es, wenn das Verstellglied einen im Wesentlichen U-förmigen Querschnitt mit zwei die Angriffsflächen ausbildenden Schenkeln aufweist, welche in einem Abstand voneinander angeordnet sind, welcher größer ist, als die Breite des zweiten Teiles des Nockens. Das Verstellglied ist nur auf den ersten Teil des verschiebbaren Nockens wirksam und mit einem U-förmigen Querschnitt ausgebildet, in welchen die Nockenerhebung des zweiten Teiles eintauchen kann, so dass in der Arbeitstaktphase der Verbrennungskraftmaschine kein Ventilhub stattfinden kann.It when the adjusting member has a substantially U-shaped cross-section with two legs forming the engagement surfaces, which are arranged at a distance from one another, which is greater than the width of the second part of the cam is very advantageous. The adjusting member is effective only on the first part of the slidable cam and formed with a U-shaped cross section, in which the cam lobe of the second part can dip, so that no valve lift can take place in the working stroke phase of the internal combustion engine.

Um eine einfache Montage der Einzelteile des Nockens auf der Nockenwelle zu ermöglichen, ist es besonders vorteilhaft, wenn zumindest eine Grundkreisscheibe eine radiale Ausnehmung zur Montage eines Stiftes aufweist, wobei vorzugsweise Ausnehmungen der einen Grundkreisscheibe versetzt zu den Ausnehmungen der anderen Grundkreisscheibe angeordnet sind. Dadurch, dass die radialen Nuten in den beiden Grundkreisscheiben wechselweise vorgesehen sind, wird die Anlage des Ventilstellgliedes an den Grundkreisscheiben nicht unterbrochen und somit Unstetigkeiten vermieden.In order to enable a simple assembly of the individual parts of the cam on the camshaft, it is particularly advantageous if at least one base disc has a radial recess for mounting a pin, wherein preferably recesses of one base disc are offset from the recesses of the other base disc. The fact that the radial grooves are provided alternately in the two base disks, the system of the valve actuator is not interrupted at the base disks and thus discontinuities avoided.

Im Rahmen der Erfindung kann weiters vorgesehen sein, dass zumindest eine Grundkreisscheibe eine Rampenerhöhung aufweist, welche gemeinsam mit der Nockenerhebung des zweiten Teiles des Nockens einen Gesamtnocken bildet. Die Rampenerhöhung der Grundkreisscheiben bilden gemeinsam mit der Nockenerhebung des verschiebbaren Nockens den Gesamtnocken aus. Durch die Rampenerhöhungen der Grundkreisscheiben kann auch eine definierte Basisöffnung des Gaswechselventils erzeugt werden.In the context of the invention may further be provided that at least one base disc has a Rampenerhöhung, which forms a total cam together with the cam lobe of the second part of the cam. The Rampenerhöhung the base circular discs form together with the cam lobe of the sliding cam from the total cam. Due to the Rampenerhöhungen the base circular disks and a defined base opening of the gas exchange valve can be generated.

Im Rahmen der Erfindung ist weiters vorgesehen, dass die Gegenfläche des ersten Teiles eine von einer Zylinderfläche abweichende Form aufweist und eine Steuerfläche definiert, so dass die Ventilhubkurve des zu betätigenden Hubventils sich aus der Form der Gegenfläche des ersten Teiles und der Form der Nockenerhebung des zweiten Teiles des Nockens zusammensetzt, wobei vorzugsweise die Gegenfläche und die Nockenerhebung des Nockens so geformt sind, dass die Ventilhubkurve insbesondere im Bereich des Überganges zwischen dem Grundkreis der Grundkreisscheiben zur Nockenerhebung des Nockens stetig verläuft.In the context of the invention, it is further provided that the counter surface of the first part has a different shape from a cylindrical surface and defines a control surface, so that the Ventilhubkurve of the actuated lift valve from the shape of the mating surface of the first part and the shape of the cam lobe of the second Part of the cam composed, wherein preferably the counter surface and the cam lobe of the cam are formed so that the valve lift curve, in particular in the region of the transition between the base circle of the base discs for cam lobing steadily.

Die vollvariable Ventilbetätigung kann insbesondere dazu eingesetzt werden, um den Startvorgang bei einer Diesel-Brennkraftmaschine zu erleichtern. Um die Verdichtungsendtemperatur zu erhöhen, kann dabei vorgesehen, dass während der Startphase und/oder während Betriebsphasen mit niedrigem Verdichtungsverhältnis der Einlassventilöffnungszeitpunkt nach spät und/oder der Einlassschließzeitpunkt nach früh verstellt wird. Dadurch können ausreichende Zündbedingungen bei abgesenktem Verdichtungsverhältnisse erzielt werden. Die Verdichtungsendtemperatur kann dabei wesentlich erhöht werden, wenn ein mehrmaliges Verdichten mit Rückschüben des Zylinderinhaltes in das Saugrohr erfolgt. Die Verschiebung des Öffnungszeitpunktes bzw. des Schließzeitpunktes kann dabei bis zu 120° Kurbelwinkel oder mehr betragen. Messungen haben gezeigt, dass sich eine signifikante Erhöhung der Ladungstemperatur im Bereich des oberen Totpunktes der Verdichtung von beispielsweise 70° bis 120°, abhängig von der Drehzahl, erzielen lassen.The fully variable valve actuation can be used in particular to facilitate the starting process in a diesel internal combustion engine. In order to increase the compression end temperature, it may be provided that during the start phase and / or during phases of operation with a low compression ratio the intake valve opening time is retarded and / or the intake closing time is advanced. This allows sufficient ignition conditions be achieved with lowered compression ratios. The compression end temperature can be substantially increased if a repeated compression takes place with retractions of the cylinder contents in the intake manifold. The shift of the opening time or the closing time can be up to 120 ° crank angle or more. Measurements have shown that a significant increase in the charge temperature in the region of top dead center of the compression of, for example, 70 ° to 120 °, depending on the speed can be achieved.

Die Erfindung wird im Folgenden anhand der Figuren näher erläutert. Es zeigen

Fig. 1
die erfindungsgemäße Ventiltriebsvorrichtung in einem Schnitt gemäß der Linie I-I in Fig. 2 bei Verstellbeginn,
Fig. 2
die Ventiltriebsvorrichtung aus Fig. 1 in einem Schnitt gemäß der Linie II-II in Fig. 1,
Fig. 3
die Ventiltriebsvorrichtung in einer Hubstellung in einem Schnitt gemäß der Linie III-III in Fig. 4,
Fig. 4
diese Ventiltriebsvorrichtung in einem Schnitt gemäß der Linie IV-IV in Fig. 3,
Fig. 5
die Ventiltriebsvorrichtung in der Ruhestellung in einem Schnitt gemäß der Linie V-V in Fig. 6; und
Fig. 6
die Ventiltriebsvorrichtung in einem Schnitt gemäß der Linie VI-VI in Fig. 5.
The invention will be explained in more detail below with reference to FIGS. Show it
Fig. 1
the valve drive device according to the invention in a section along the line II in Fig. 2 at the beginning of adjustment,
Fig. 2
the valvetrain device off Fig. 1 in a section along the line II-II in Fig. 1 .
Fig. 3
the valve drive device in a stroke position in a section along the line III-III in Fig. 4 .
Fig. 4
this valve drive device in a section along the line IV-IV in Fig. 3 .
Fig. 5
the valve drive device in the rest position in a section along the line VV in Fig. 6 ; and
Fig. 6
the valve drive device in a section along the line VI-VI in Fig. 5 ,

In den Figuren ist jeweils eine Nockenwelle 1 einer Brennkraftmaschine mit einer variablen Ventiltriebsvorrichtung 2 dargestellt. Die Ventiltriebsvorrichtung 2 weist zwei fest mit der Nockenwelle 1 verbundene Grundkreisscheiben 3, einen im Wesentlichen radial auf der Nockenwelle 1 verschiebbaren Nocken 4 und ein direkt auf den Nocken 4 einwirkendes Verstellglied 5 auf.In the figures, a camshaft 1 of an internal combustion engine with a variable valve drive device 2 is shown in each case. The valve drive device 2 has two integral with the camshaft 1 base circular disks 3, a substantially radially displaceable on the camshaft 1 cam 4 and a directly acting on the cam 4 adjusting 5.

Der Nocken 4 besteht aus zwei ineinander geschobenen Teilen, und zwar einem vom Verstellglied 5 beaufschlagten ersten Teil 6 und einem die Nockenerhebung 7 aufweisenden zweiten Teil 8. Erster und zweiter Teil 6, 8 umgreifen Mitnahmeflächen 9 der Nockenwelle 1, wobei der Nocken 4 im Bereich der Mitnahmeflächen 9 Gleitflächen 10 aufweisen. Der erste Teil 6 weist einen gabelförmigen Querschnitt auf, welcher den zweiten Teil 8 umfasst, wie aus Fig. 2 erkennbar ist. Diametral bezüglich der Nockenerhebung 7 weist der erste Teil 6 eine Steuerkurve 11, auf welche das Verstellglied 5 auf den Nocken 4 einwirkt. Das Verstellglied 5 weist im Ausführungsbeispiel eine Betätigungsrolle 12 mit einem im Wesentlichen U-förmigen Querschnitt mit zwei Schenkeln 23 auf, welche durch Ränder 13 der der Betätigungsrolle 12 gebildet werden. Die Ränder 13 wirken über Angriffsflächen 21 auf durch die Steuerflächen 11 des ersten Teiles 6 des Nockens 4 gebildete Gegenflächen 22 ein. Der Abstand a der Ränder 13 entspricht mindestens der Breite b des zweiten Teiles 8, so dass in der Arbeitstaktphase der Brennkraftmaschine kein Ventilhub stattfinden kann.The cam 4 consists of two nested parts, one acted upon by the adjusting member 5 first part 6 and a cam lobe 7 having second part 8. First and second part 6, 8 engage driving surfaces 9 of the camshaft 1, wherein the cam 4 in the area the driving surfaces have 9 sliding surfaces 10. The first part 6 has a fork-shaped cross section, which comprises the second part 8, as seen from Fig. 2 is recognizable. Diametrically with respect to the cam elevation 7, the first part 6 has a control cam 11, on which the adjusting member 5 acts on the cam 4. The adjusting member 5 has in the embodiment, an actuating roller 12 with a in Substantially U-shaped cross section with two legs 23, which are formed by edges 13 of the actuating roller 12. The edges 13 act on engagement surfaces 21 on by the control surfaces 11 of the first part 6 of the cam 4 formed counter-surfaces 22 a. The distance a of the edges 13 corresponds at least to the width b of the second part 8, so that no valve lift can take place in the working phase of the internal combustion engine.

Der Nocken 4 ist über ein elastisches Element 14 vorgespannt, wobei das elastische Element 14 den Nocken 4 in die in Fig. 5 und Fig. 6 dargestellte Ruhelage drückt, in welcher nur die Grundkreisscheiben 3 auf das Ventilstellglied 15 einwirken.The cam 4 is biased by an elastic member 14, wherein the elastic member 14, the cam 4 in the in Fig. 5 and Fig. 6 shown rest position presses, in which only the base circular disks 3 act on the valve actuator 15.

Der erste Teil 6 und der zweite Teil 8 des Nockens 4 stützen sich zueinander ab und sind mit Stiften 16 miteinander verbunden. Über das elastische Element 14 wird der Nocken 4 auf eine Null-Hub-Lage gedrückt, wenn über die Zustellrolle 12 kein Kraftschluss erfolgt. Für die Stifte 16 sind in den Grundkreisscheiben 3 radiale Montagenuten 17 vorgesehen. Die Montagenuten 17 sind in den Grundkreisscheiben 3 wechselweise angeordnet, um die Anlage des Ventilstellgliedes 15 an den Grundkreisscheiben 3 nicht zu unterbrechen.The first part 6 and the second part 8 of the cam 4 are based on each other and are connected to each other with pins 16. Via the elastic element 14, the cam 4 is pressed to a zero-stroke position, if there is no frictional connection via the feed roller 12. For the pins 16 3 radial mounting grooves 17 are provided in the base disks. The mounting grooves 17 are alternately arranged in the base disks 3 so as not to interrupt the contact of the valve actuator 15 to the base disks 3.

Die Betätigungsrolle 12 ist also so ausgebildet, dass die Nockenerhebung 7 in den Freiraum 18 zwischen den Rändern 13 eintaucht, wenn sich die Brennkraftmaschine im Arbeitstakt befindet. Außerhalb der Zusteuerungsphase und des Ventilhubes ist kein Kontakt zwischen der Betätigungsrolle 12 und dem Nocken 4 vorhanden, so dass das Ventilstellglied 15, welches durch einen Stößel, Schlepphebel oder Kipphebel gebildet sein kann, in Berührungskontakt mit den auf der Nockenwelle 4 außerhalb der Betätigungsrolle 12 angeordneten fixen Grundkreisscheiben 3 steht.The actuating roller 12 is thus designed so that the cam lobe 7 dips into the free space 18 between the edges 13 when the internal combustion engine is in the working cycle. Outside the Zusüuerungsphase and the valve lift is no contact between the actuating roller 12 and the cam 4 is present, so that the valve actuator 15, which may be formed by a plunger, finger lever or rocker arm, in contact with the arranged on the camshaft 4 outside of the actuating roller 12 fixed base disks 3 is.

Die Mitnahmeflächen 9, sowie die Gleitflächen 10, sind bogenförmig ausgeführt. Ihre Winkellage und ihr Radius ist so gewählt, dass eine möglichst reibungsarme Verstellung möglich wird, und dass in jedem Falle Selbsthemmung, insbesondere zu Beginn der Verschiebung des Nockens 4, vermieden wird. Über eine zentrale Bohrung 18 in der Nockenwelle 1 kann problemlos Drucköl zur Schmierung der Gleitflächen 10 zugeführt werden.The driving surfaces 9, as well as the sliding surfaces 10, are arcuate. Your angular position and its radius is chosen so that the lowest possible adjustment possible, and that in any case, self-locking, especially at the beginning of the displacement of the cam 4, is avoided. Via a central bore 18 in the camshaft 1, pressure oil for lubricating the sliding surfaces 10 can be supplied without problems.

Die Grundkreisscheiben 3 können einen Rampenbereich 19 aufweisen, welcher gemeinsam mit der Nockenerhebung 7 des verschiebbaren Nockens 4 den Gesamtnocken bildet. Der Rampenbereich 19 definiert einen Mindesthub des nicht weiter dargestellten Gaswechselventils und ermöglicht einen gleichmäßigen Übergang vom Grundkreis 20 der Grundkreisscheibe 3 auf die Nockenerhebung 7 und umgekehrt. Die Form der Ventilhubkurve wird durch das Zusammenwirken der Steuerkurve 11 mit der Nockenerhebung 7 des verschiebbaren Nockens 4 während der Hubphase definiert. Durch entsprechende Formgebung der Steuerkurve 11 und der Nockenerhebung 7 wird ein gleichmäßiger Übergang vom Grundkreis 20 auf die Nockenerhebung 7 und umgekehrt ermöglicht.The base circular disks 3 may have a ramp region 19 which, together with the cam lobe 7 of the displaceable cam 4, forms the total cam. The ramp region 19 defines a minimum stroke of the gas exchange valve, not shown, and allows a smooth transition from the base circle 20 of the base plate 3 on the cam elevation 7 and vice versa. The shape of the valve lift curve is due to the interaction the control cam 11 defined with the cam lobe 7 of the displaceable cam 4 during the lifting phase. By appropriate shaping of the control cam 11 and the cam elevation 7, a uniform transition from the base circle 20 to the cam elevation 7 and vice versa is made possible.

Fig. 1 zeigt die Ventiltriebsvorrichtung 2 zu Verstellbeginn. Die Betätigungsrolle 12 wird aus der durch Bezugszeichen 12' bezeichneten und strichliert angedeuteten Ruhelage in Richtung der Nockenwelle 1 entsprechend dem Pfeil P1 verschoben, so dass die Ränder 13 der Betätigungsrolle 12 auf die Steuerkurve 11 des ersten Teiles 6 des Nockens 4 einwirken und den Nocken 4 aus der Ruheposition entgegen der Kraft des elastischen Elementes 14 in den Fig. 3 und Fig. 4 dargestellte Hubposition auslenken. In dieser Hubposition überragt die Nockerhebung 7 die Grundkreisscheiben 3 und wirkt somit auf das Ventilstellglied 15 ein. Die Nockenwelle 1 läuft dabei in der durch den Pfeil P2 bezeichneten Drehrichtung um. Fig. 1 shows the valve drive device 2 to Verstellbeginn. The actuating roller 12 is moved from the rest position indicated by reference numeral 12 'and indicated by dashed lines in the direction of the camshaft 1 according to the arrow P 1 , so that the edges 13 of the actuating roller 12 act on the control cam 11 of the first part 6 of the cam 4 and the cam 4 from the rest position against the force of the elastic element 14 in the FIG. 3 and FIG. 4 deflected illustrated stroke position. In this lifting position, the cam elevation 7 projects beyond the base circular disks 3 and thus acts on the valve actuator 15. The camshaft 1 runs in the direction indicated by the arrow P 2 rotation.

Die Montage des ersten Teiles 6 und des zweiten Teiles 8 auf der Nockenwelle 1 erfolgt durch Aufschieben derselben auf die Mitnahmeflächen 9 von verschiedenen Seiten. Wird der Nocken 4 entgegen der Kraft des elastischen Elementes 14 in die in Fig. 3 dargestellte Hubposition gedrückt, so können die Stifte 16 durch die radialen Nuten in Richtung der Achse 1a der Nockenwelle 1 eingesetzt werden.The assembly of the first part 6 and the second part 8 on the camshaft 1 is carried out by pushing the same on the driving surfaces 9 from different sides. If the cam 4 against the force of the elastic element 14 in the in Fig. 3 Pressed stroke position shown, the pins 16 can be used by the radial grooves in the direction of the axis 1 a of the camshaft 1.

Der Vorteil des variablen Ventiltriebes 2 ist, dass durch die externe Betätigung mittels des Verstellgliedes 5 eine hohe Zahl an Variationsmöglichkeiten möglich ist. Das Verstellglied 5 kann pneumatisch, hydraulisch, elektrisch, elektromagnetisch, mechanisch oder in Kombination davon betätigt werden.The advantage of the variable valve train 2 is that a large number of possible variations is possible by the external actuation by means of the adjusting member 5. The adjusting member 5 can be operated pneumatically, hydraulically, electrically, electromagnetically, mechanically or in combination thereof.

Die mit der Anmeldung eingereichten Patentansprüche sind Formulierungsvorschläge ohne Präjudiz für die Erzielung weitergehenden Patentschutzes. Die Anmelderin behält sich vor, noch weitere, bisher nur in der Beschreibung und/oder Zeichnungen offenbarte Merkmale zu beanspruchen.The claims filed with the application are formulation proposals without prejudice to the achievement of further patent protection. The Applicant reserves the right to claim further features which have hitherto been disclosed only in the description and / or drawings.

In Unteransprüchen verwendete Rückbeziehungen weisen auf die weitere Ausbildung des Gegenstandes des Hautanspruches durch die Merkmale des jeweiligen Unteranspruches hin; sie sind nicht als ein Verzicht auf die Erzielung eines selbständigen, gegenständlichen Schutzes für die Merkmale der rückbezogenen Unteransprüche zu verstehen.Relationships used in dependent claims point to the further development of the subject matter of the skin claim by the features of the respective subclaim; they should not be construed as a waiver of the attainment of independent, objective protection for the features of the dependent claims.

Die Gegenstände dieser Unteransprüche bilden jedoch auch selbständige Erfindungen, die eine von den Gegenständen der vorhergehenden Unteransprüche unabhängige Gestaltung aufweisen.However, the subjects of these subclaims also form independent inventions which have an independent of the subjects of the preceding subclaims design.

Die Erfindung ist auch nicht auf das (die) Ausführungsbeispiel(e) der Beschreibung beschränkt. Vielmehr sind im Rahmen der Erfindung zahlreiche Abänderungen und Modifikationen möglich, insbesondere solche Varianten, Elemente und Kombinationen und/oder Materialien, die zum Beispiel durch Kombination oder Abwandlung von einzelnen in Verbindung mit den in der allgemeinen Beschreibung Ausführungsformen sowie den Ansprüchen beschriebenen und in den Zeichnungen enthaltenen Merkmalen bzw. Elementen oder Verfahrensschritten erfinderisch sind und durch kombinierbare Merkmale zu einem neuen Gegenstand oder zu neuen Verfahrensschritten bzw. Verfahrensschrittfolgen führen, auch soweit sie Herstell-, Prüf- und Arbeitsverfahren betreffen.The invention is not limited to the embodiment (s) of the description. Rather, numerous modifications and variations are possible within the scope of the invention, in particular those variants, elements and combinations and / or materials, for example, by combination or modification of individual in conjunction with those described in the general description embodiments and the claims and in the drawings contained features or elements or process steps are inventive and lead by combinable features to a new subject or to new process steps or process steps, even if they concern manufacturing, testing and working procedures.

Claims (11)

  1. Internal combustion engine comprising a variable valve drive mechanism provided with at least one camshaft (1) with at least one cam arrangement (2), which comprises a cam (4) that is movable essentially radially relative to the camshaft, and at least one, preferentially two, base circle disk(s) (3) fixed on the camshaft, with the cam being actuated by an adjusting element (5) located beside the camshaft, characterised in that the cam (4) is borne via sliding surfaces (10) on circular guiding surfaces (9) of the camshaft (1).
  2. Internal combustion engine, in particular according to claim 1, characterised in that the cam (1) is brought from an inactive position to a lifting position by the adjusting element (5) prior to or during a lifting phase.
  3. Internal combustion engine, in particular according to claim 1 or 2, characterised in that the cam (4) which is movable on the camshaft (1) in essentially radial direction is held against the camshaft (1) in the opposite direction of the lifting position by a spring element (14) and can be retracted to its inactive position after the lifting phase by said spring element (14), the cam (4) in its inactive position being preferably within the base circle of the base circle disk (3).
  4. Internal combustion engine, in particular according to any of claims 1 to 3, characterised in that the cam (4) comprises two parts, a first part (6), which is actuated by the adjusting element (5), being essentially forkshaped as seen from the side and gripping a second part (8) forming the cam lobe, and first and second part preferably being held together by pins (16).
  5. Internal combustion engine, in particular according to any of claims 1 to 4, characterised in that the adjusting element (5) has at least one working surface (21), which interacts with a corresponding mating surface (22) on the first part (6) of the cam.
  6. Internal combustion engine, in particular according to claim 5, characterised in that the adjusting element (5) has an essentially U-shaped cross-section with the two legs of the U as working surfaces (21), the legs having a distance from each other which is greater than the width of the second part (8) of the cam.
  7. Internal combustion engine, in particular according to claim 5 or 6, characterised in that the adjusting element (5) is configured as an actuating roller (12), which actuating roller (12) has at least one flange-like rim (13) serving as the working surface (21).
  8. Internal combustion engine, in particular according to any of claims 4 to 7, characterised in that at least one base circle disk (3) has a radial groove (17) into which a pin (16) can be inserted, the grooves (17) of one base circle disk (3) preferably being displaced relative to the grooves (17) of the other base circle disk (3).
  9. Internal combustion engine, in particular according to any of claims 1 to 8, characterised in that at least one base circle disk (3) has a ramp-shaped elevation (19), which together with the cam lobe (7) of the second part (8) of the cam defines the lift curve of at least one gas exchange valve.
  10. Internal combustion engine, in particular according to any of claims 1 to 8, characterised in that the mating surface (22) of the first part (6) of the cam deviates from a strictly cylindrical shape and defines a control surface, such that the valve lift curve of the corresponding gas exchange valve is generated by the shape of the control surface of the first part (6) and the shape of the cam lobe of the second part (8) of the cam.
  11. Internal combustion engine, in particular according to any of claims 1 to 9, characterised in that the control surface and the cam lobe of the cam (4) are shaped in such a way that the valve lift curve is continuous, especially in the region of transition between the base circle of the base circle disks and the cam lobe of the cam.
EP04737352A 2003-06-24 2004-06-24 Internal combustion engine Expired - Lifetime EP1636466B1 (en)

Applications Claiming Priority (2)

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AT0043303U AT6651U1 (en) 2003-06-24 2003-06-24 VARIABLE VALVE DRIVE DEVICE FOR AN INTERNAL COMBUSTION ENGINE
PCT/AT2004/000218 WO2004113688A2 (en) 2003-06-24 2004-06-24 Internal combustion engine

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EP1636466A2 EP1636466A2 (en) 2006-03-22
EP1636466B1 true EP1636466B1 (en) 2008-07-23

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AT (2) AT6651U1 (en)
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JP5488512B2 (en) * 2011-03-28 2014-05-14 三菱自動車工業株式会社 Cam structure

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CN1839249A (en) 2006-09-27
AT6651U1 (en) 2004-01-26
WO2004113688A3 (en) 2005-06-09
US7424877B2 (en) 2008-09-16
WO2004113688A2 (en) 2004-12-29
ATE402327T1 (en) 2008-08-15
US20060169235A1 (en) 2006-08-03
CN100443696C (en) 2008-12-17
EP1636466A2 (en) 2006-03-22
DE502004007682D1 (en) 2008-09-04

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