EP1636466A2 - Internal combustion engine - Google Patents

Internal combustion engine

Info

Publication number
EP1636466A2
EP1636466A2 EP04737352A EP04737352A EP1636466A2 EP 1636466 A2 EP1636466 A2 EP 1636466A2 EP 04737352 A EP04737352 A EP 04737352A EP 04737352 A EP04737352 A EP 04737352A EP 1636466 A2 EP1636466 A2 EP 1636466A2
Authority
EP
European Patent Office
Prior art keywords
cam
combustion engine
internal combustion
camshaft
particular according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04737352A
Other languages
German (de)
French (fr)
Other versions
EP1636466B1 (en
Inventor
Johann Wagner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AVL List GmbH
Original Assignee
AVL List GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by AVL List GmbH filed Critical AVL List GmbH
Publication of EP1636466A2 publication Critical patent/EP1636466A2/en
Application granted granted Critical
Publication of EP1636466B1 publication Critical patent/EP1636466B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 with a variable valve drive device with at least one camshaft with at least one cam arrangement, which has a cam which can be displaced essentially radially with respect to the camshaft and at least one, preferably two, base circle disks fixed to the camshaft
  • 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 stroke section which moves back and forth in the direction of the valve to be actuated, with a device being provided which engages the cam with the camshaft and disengages the cam from the camshaft , which is done in accordance with engine operating conditions.
  • the cam is moved hydraulically.
  • a cam-equipped valve actuation for a globe valve which contains a cam with a rigid component which can be adjusted in the radial direction between a retracted and an extended position, which is guided on the associated camshaft and the stops for limiting its exit movement assigned.
  • the cam is displaced 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 the hydraulic actuating means must be provided at relatively high pressure in order to actively actuate the cam.
  • variable valve trains are usually only suitable for a certain type of actuation, i.e. either hydraulic, mechanical or electrical actuation.
  • JP 1-1117840 A also discloses the change in the intake timing during the starting phase.
  • the object of the invention is to avoid these disadvantages and to propose a simple variable valve drive device which is suitable for external actuation with various actuating means, in particular to facilitate the starting process of an internal combustion engine.
  • the cam can be controlled by an adjusting member arranged on the side of the camshaft.
  • the radially displaceable cam is thus controlled directly by the adjusting element arranged outside the camshaft.
  • the radially displaceable cam can be controlled by the adjusting member in the lifting position before or during the lifting phase.
  • the adjusting member is preferably 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 into its starting position behind the base circle by this elastic element after the lifting phase.
  • the cam is mounted on circular driving surfaces of the camshaft via sliding surfaces.
  • the radius and angular position of the sliding surfaces are arranged in such a way that no self-locking occurs when the cam begins to move.
  • the cam is designed in two parts, a first part acted upon by the adjusting member being viewed in a side view, being essentially fork-shaped and enclosing a second part having a cam elevation, the first and second part preferably using pins are interconnected.
  • the first part acted upon by the adjusting member surrounds the second part, which has a cam elevation surface, in a U-shape and is connected to it by two pins after being pushed onto the camshaft, so that the first and second part of the cam form a cam unit.
  • the adjustment member has at least one engagement surface which interacts with a corresponding corresponding counter surface of the first part of the cam. It is very advantageous if the adjusting member has an essentially U-shaped cross section with two legs forming the contact surfaces, which are arranged at a distance from one another which is greater than the width of the second part of the cam.
  • the adjusting member is only effective on the first part of the displaceable cam and is designed with a U-shaped cross section, in which the cam elevation of the second part can be immersed, so that no valve lift can take place in the working cycle phase of the internal combustion engine.
  • At least one base circular disc has a radial recess for mounting a pin, recesses in one base circular disc preferably being offset from the recesses in the other base circular disc.
  • the radial grooves are alternately provided in the two base circle disks, the contact of the valve actuator on the base circle disks is not interrupted and thus discontinuities are avoided.
  • At least one base circle disc has a ramp increase which, together with the cam elevation of the second part of the cam, forms an overall cam.
  • the ramp increase of the base circle discs together with the cam elevation of the displaceable cam form the overall cam.
  • a defined base opening of the gas exchange valve can also be generated by the ramp increases in the base circular disks.
  • the counter surface of the first part has a shape deviating from a cylindrical surface and defines a control surface, so that the valve lift curve of the lift valve to be actuated results from the shape of the counter surface of the first part and the shape of the cam elevation of the second Part of the cam is composed, wherein preferably the counter surface and the cam elevation of the cam are shaped such that the valve lift curve runs continuously, especially in the area of the transition between the base circle of the base circle disks for cam elevation of the cam.
  • the fully variable valve actuation can be used in particular to facilitate the starting process for a diesel internal combustion engine.
  • the inlet valve opening time is adjusted late and / or the inlet closing time is adjusted early.
  • Sufficient ignition conditions can be achieved with reduced compression ratios.
  • the final compression temperature can be increased significantly if the cylinder contents are compressed several times with pushing back into 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 area of the top dead center of the compression, for example 70 ° to 120 °, can be achieved, depending on the speed.
  • FIG. 1 shows the valve drive device according to the invention in a section along the line I-I in Fig. 2 at the beginning of the adjustment
  • FIG. 2 shows the valve drive device from FIG. 1 in a section along the line II-II in FIG. 1,
  • FIG. 3 shows the valve drive device in a lifting position in a section along the line III-III in FIG. 4,
  • Figure 5 shows the valve drive device in the rest position in a section along the line V-V in Fig. 6 .
  • FIG. 6 shows the valve drive device in a section along the line VI-VI in FIG. 5th
  • a camshaft 1 of an internal combustion engine with a variable valve drive device 2 is shown in the figures.
  • the valve drive device 2 has two base circular disks 3 fixedly connected to the camshaft 1, a cam 4 which can be displaced essentially radially on the camshaft 1 and an adjusting member 5 which acts directly on the cam 4.
  • the cam 4 consists of two parts pushed into one another, namely a first part 6 acted on by the adjusting member 5 and a second part 8 having the cam elevation 7.
  • the first and second parts 6, 8 encompass driving surfaces 9 of the camshaft 1, the cam 4 in the region of the driving surfaces 9 have sliding surfaces 10.
  • the first part 6 has a fork-shaped cross section, which comprises the second part 8, as can be seen from FIG. 2.
  • 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 an actuating roller 12 with an im Mainly U-shaped cross-section with two legs 23, which are formed by edges 13 of the actuating roller 12.
  • edges 13 act via engagement surfaces 21 on counter surfaces 22 formed by the control surfaces 11 of the first part 6 of the cam 4.
  • the distance a between 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 work cycle phase of the internal combustion engine.
  • the cam 4 is prestressed via an elastic element 14, the elastic element 14 pressing the cam 4 into the rest position shown in FIGS. 5 and 6, 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 supported against one another and are connected to one another by pins 16.
  • the cam 4 is pressed to a zero-stroke position via the elastic element 14 if no non-positive connection takes place via the feed roller 12.
  • radial mounting grooves 17 are provided in the base circular disks.
  • the mounting grooves 17 are arranged alternately in the base circular disks 3 so as not to interrupt the contact of the valve actuator 15 on the base circular disks 3.
  • the actuating roller 12 is thus designed such that the cam elevation 7 dips into the space 18 between the edges 13 when the internal combustion engine is in the work cycle. Outside the control phase and the valve lift, there is no contact between the actuating roller 12 and the cam 4, so that the valve actuator 15, which can be formed by a tappet, rocker arm or rocker arm, is arranged in contact contact with those on the camshaft 4 outside the actuating roller 12 fixed base circle 3 stands.
  • the driving surfaces 9, as well as the sliding surfaces 10, are designed in an arc shape. Their angular position and their radius are selected in such a way that adjustment with as little friction as possible is possible and that in any case self-locking, in particular at the beginning of the displacement of the cam 4, is avoided. Via a central bore 18 in the camshaft 1, pressure oil for the lubrication of the sliding surfaces 10 can be supplied without problems.
  • the base circular disks 3 can have a ramp area 19 which, together with the cam elevation 7 of the displaceable cam 4, forms the overall cam.
  • the ramp area 19 defines a minimum stroke of the gas exchange valve (not shown further) and enables a smooth transition from the base circle 20 of the base disk 3 to the cam elevation 7 and vice versa.
  • the shape of the valve lift curve is due to the interaction the control curve 11 with the cam elevation 7 of the displaceable cam 4 defined during the lifting phase. Appropriate shaping of the control cam 11 and the cam elevation 7 enables a smooth transition from the base circle 20 to the cam elevation 7 and vice versa.
  • the actuating roller 12 is shifted from the rest position indicated by the reference numeral 12 'and indicated by dashed lines in the direction of the camshaft 1 in accordance with the arrow P *, so that the edges 13 of the actuating roller 12 act on the cam 11 of the first part 6 of the cam 4 and the cam 4 deflect from the rest position against the force of the elastic element 14 in the lifting position shown in FIGS. 3 and 4.
  • the cam lift 7 projects beyond the base circular disks 3 and thus acts on the valve actuator 15.
  • the camshaft 1 rotates in the direction of rotation indicated by the arrow P 2 .
  • the first part 6 and the second part 8 are assembled on the camshaft 1 by pushing them onto the driving surfaces 9 from different sides. If the cam 4 is pressed against the force of the elastic element 14 into the lifting position shown in FIG. 3, the pins 16 can be inserted through the radial grooves in the direction of the axis la of the camshaft 1.
  • variable valve train 2 The advantage of the variable valve train 2 is that the external actuation by means of the adjusting member 5 enables a large number of possible variations.
  • the adjusting member 5 can be operated pneumatically, hydraulically, electrically, electromagnetically, mechanically or in combination thereof.
  • references used in the subclaims indicate the further development of the subject matter of the skin claim through the features of the respective subclaim; they are not to be understood as a waiver of the achievement of independent, objective protection for the characteristics of the related subclaims.

Landscapes

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

Abstract

The invention relates to an internal combustion engine comprising a variable valve drive device provided with at least one camshaft having at least one cam arrangement. Said cam arrangement comprises a cam which can be displaced essentially radially in relation to the camshaft, and at least one, preferably two, base circle disks fixed to the camshaft.

Description

BrennkraftmaschineInternal combustion engine
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 with a variable valve drive device with at least one camshaft with at least one cam arrangement, which has a cam which can be displaced essentially radially with respect to the camshaft and at least one, preferably two, base circle disks fixed to the camshaft
Aus der DE 100 53 776 AI 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 DE 100 53 776 AI 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 stroke section which moves back and forth in the direction of the valve to be actuated, with a device being provided which engages the cam with the camshaft and disengages the cam from the camshaft , which is done in accordance with engine operating conditions. The cam is moved hydraulically.
Aus der DE 42 22 477 AI 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 DE 42 22 477 AI a cam-equipped valve actuation for a globe valve is known, which contains a cam with a rigid component which can be adjusted in the radial direction between a retracted and an extended position, which is guided on the associated camshaft and the stops for limiting its exit movement assigned. The cam is displaced 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 the hydraulic actuating means must be provided at relatively high pressure in order to actively actuate the cam. In addition, variable valve trains are usually only suitable for a certain type of actuation, i.e. either hydraulic, mechanical or electrical actuation.
Aus den Veröffentlichungen DE 41 41 482 AI, DE 37 37 824 AI und DE 199 08 435 AI ist es bekannt, beim Startvorgang Impulsaufladung durchzuführen bzw. den Einlassbeginn in der Startphase zu verzögern, um den Startvorgang zu vereinfachen.From publications DE 41 41 482 AI, DE 37 37 824 AI and DE 199 08 435 AI it is known to carry out pulse charging during the starting process or to delay the start of admission in the starting phase in order to simplify the starting process.
Weiters beschreibt die Veröffentlichung DE 102 17 695 AI 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. 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.Furthermore, the publication DE 102 17 695 AI describes a starting method with changed control times of the inlet valves to reduce the compression work during starting. JP 1-1117840 A also discloses the change in the intake timing during the starting phase. The object of the invention is to avoid these disadvantages and to propose a simple variable valve drive device which is suitable for external actuation with various 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 Versteilglied 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 Versteilgliedern eingeschränkt.According to the invention, this is achieved in that the cam can be controlled by an adjusting member arranged on the side of the camshaft. The radially displaceable cam is thus controlled directly by the adjusting element arranged outside the camshaft. This has the advantage that, in addition to hydraulic or pneumatic actuators, purely mechanical or electrical or electromagnetic actuators can also be used. The variable valve drive device is therefore not restricted to a specific type of adjusting members.
Der radial verschiebbare Nocken kann jeweils vor oder auch während der Hubphase vom Versteilglied in die Hubposition gesteuert werden. Vorzugsweise ist das Versteilglied durch eine Betätigungsrolle gebildet, welche beispielsweise über einen Exzenter verstellt werden kann.The radially displaceable cam can be controlled by the adjusting member in the lifting position before or during the lifting phase. The adjusting member is preferably 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 into its starting position behind the base circle by this elastic element after the lifting phase.
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 the cam to be moved without jamming, it is advantageous if the cam is mounted on circular driving surfaces of the camshaft via sliding surfaces. The radius and angular position of the sliding surfaces are arranged in such a way that no self-locking occurs when the cam begins to move.
In einer bevorzugten Ausführungsvariante der Erfindung ist vorgesehen, dass der Nocken zweiteilig ausgeführt ist, wobei ein vom Versteilglied 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 variant of the invention it is provided that the cam is designed in two parts, a first part acted upon by the adjusting member being viewed in a side view, being essentially fork-shaped and enclosing a second part having a cam elevation, the first and second part preferably using pins are interconnected. The first part acted upon by the adjusting member surrounds the second part, which has a cam elevation surface, in a U-shape and is connected to it 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. 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.The adjustment member has at least one engagement surface which interacts with a corresponding corresponding counter surface of the first part of the cam. It is very advantageous if the adjusting member has an essentially U-shaped cross section with two legs forming the contact surfaces, which are arranged at a distance from one another which is greater than the width of the second part of the cam. The adjusting member is only effective on the first part of the displaceable cam and is designed with a U-shaped cross section, in which the cam elevation of the second part can be immersed, so that no valve lift can take place in the working cycle 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 Unstetig keiten vermieden.In order to enable simple assembly of the individual parts of the cam on the camshaft, it is particularly advantageous if at least one base circular disc has a radial recess for mounting a pin, recesses in one base circular disc preferably being offset from the recesses in the other base circular disc. Characterized in that the radial grooves are alternately provided in the two base circle disks, the contact of the valve actuator on the base circle disks is not interrupted and thus discontinuities are 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.Within the scope of the invention it can further be provided that at least one base circle disc has a ramp increase which, together with the cam elevation of the second part of the cam, forms an overall cam. The ramp increase of the base circle discs together with the cam elevation of the displaceable cam form the overall cam. A defined base opening of the gas exchange valve can also be generated by the ramp increases in the base circular disks.
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.Within the scope of the invention, it is further provided that the counter surface of the first part has a shape deviating from a cylindrical surface and defines a control surface, so that the valve lift curve of the lift valve to be actuated results from the shape of the counter surface of the first part and the shape of the cam elevation of the second Part of the cam is composed, wherein preferably the counter surface and the cam elevation of the cam are shaped such that the valve lift curve runs continuously, especially in the area of the transition between the base circle of the base circle disks for cam elevation of the cam.
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 Zündbe- dingungen 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 for a diesel internal combustion engine. In order to increase the compression end temperature, it can be provided that during the start phase and / or during operating phases with a low compression ratio the inlet valve opening time is adjusted late and / or the inlet closing time is adjusted early. Sufficient ignition conditions can be achieved with reduced compression ratios. The final compression temperature can be increased significantly if the cylinder contents are compressed several times with pushing back into 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 area of the top dead center of the compression, for example 70 ° to 120 °, can be achieved, depending on the speed.
Die Erfindung wird im Folgenden anhand der Figuren näher erläutert. Es zeigenThe invention is explained in more detail below with reference to the figures. Show it
Fig. 1 die erfindungsgemäße Ventiltriebsvorrichtung in einem Schnitt gemäß der Linie I-I in Fig. 2 bei Verstellbeginn,1 shows the valve drive device according to the invention in a section along the line I-I in Fig. 2 at the beginning of the adjustment,
Fig. 2 die Ventiltriebsvorrichtung aus Fig. 1 in einem Schnitt gemäß der Linie II-II in Fig. 1,2 shows the valve drive device from FIG. 1 in a section along the line II-II in FIG. 1,
Fig. 3 die Ventiltriebsvorrichtung in einer Hubstellung in einem Schnitt gemäß der Linie III-III in Fig. 4,3 shows the valve drive device in a lifting position in a section along the line III-III in FIG. 4,
Fig. 4 diese Ventiltriebsvorrichtung in einem Schnitt gemäß der Linie IV- IV in Fig. 3,4 shows this valve drive device in a section along the line IV-IV in FIG. 3,
Fig. 5 die Ventiltriebsvorrichtung in der Ruhestellung in einem Schnitt gemäß der Linie V-V in Fig. 6; undFigure 5 shows the valve drive device in the rest position in a section along the line V-V in Fig. 6 .; and
Fig. 6 die Ventiltriebsvorrichtung in einem Schnitt gemäß der Linie VI-VI in Fig. 5.6 shows the valve drive device in a section along the line VI-VI in FIG. 5th
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.A camshaft 1 of an internal combustion engine with a variable valve drive device 2 is shown in the figures. The valve drive device 2 has two base circular disks 3 fixedly connected to the camshaft 1, a cam 4 which can be displaced essentially radially on the camshaft 1 and an adjusting member 5 which acts directly on the cam 4.
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 parts pushed into one another, namely a first part 6 acted on by the adjusting member 5 and a second part 8 having the cam elevation 7. The first and second parts 6, 8 encompass driving surfaces 9 of the camshaft 1, the cam 4 in the region of the driving surfaces 9 have sliding surfaces 10. The first part 6 has a fork-shaped cross section, which comprises the second part 8, as can be seen from FIG. 2. 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. In the exemplary embodiment, the adjusting member 5 has an actuating roller 12 with an im Mainly U-shaped cross-section with two legs 23, which are formed by edges 13 of the actuating roller 12. The edges 13 act via engagement surfaces 21 on counter surfaces 22 formed by the control surfaces 11 of the first part 6 of the cam 4. The distance a between 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 work cycle 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 prestressed via an elastic element 14, the elastic element 14 pressing the cam 4 into the rest position shown in FIGS. 5 and 6, 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 supported against one another and are connected to one another by pins 16. The cam 4 is pressed to a zero-stroke position via the elastic element 14 if no non-positive connection takes place via the feed roller 12. For the pins 16 3 radial mounting grooves 17 are provided in the base circular disks. The mounting grooves 17 are arranged alternately in the base circular disks 3 so as not to interrupt the contact of the valve actuator 15 on the base circular 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 such that the cam elevation 7 dips into the space 18 between the edges 13 when the internal combustion engine is in the work cycle. Outside the control phase and the valve lift, there is no contact between the actuating roller 12 and the cam 4, so that the valve actuator 15, which can be formed by a tappet, rocker arm or rocker arm, is arranged in contact contact with those on the camshaft 4 outside the actuating roller 12 fixed base circle 3 stands.
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 designed in an arc shape. Their angular position and their radius are selected in such a way that adjustment with as little friction as possible is possible and that in any case self-locking, in particular at the beginning of the displacement of the cam 4, is avoided. Via a central bore 18 in the camshaft 1, pressure oil for the lubrication of 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 can have a ramp area 19 which, together with the cam elevation 7 of the displaceable cam 4, forms the overall cam. The ramp area 19 defines a minimum stroke of the gas exchange valve (not shown further) and enables a smooth transition from the base circle 20 of the base disk 3 to the cam elevation 7 and vice versa. The shape of the valve lift curve is due to the interaction the control curve 11 with the cam elevation 7 of the displaceable cam 4 defined during the lifting phase. Appropriate shaping of the control cam 11 and the cam elevation 7 enables a smooth transition from the base circle 20 to the cam elevation 7 and vice versa.
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 P* 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 Nockerhe- bung 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.1 shows the valve drive device 2 at the beginning of the adjustment. The actuating roller 12 is shifted from the rest position indicated by the reference numeral 12 'and indicated by dashed lines in the direction of the camshaft 1 in accordance with the arrow P *, so that the edges 13 of the actuating roller 12 act on the cam 11 of the first part 6 of the cam 4 and the cam 4 deflect from the rest position against the force of the elastic element 14 in the lifting position shown in FIGS. 3 and 4. In this stroke position, the cam lift 7 projects beyond the base circular disks 3 and thus acts on the valve actuator 15. The camshaft 1 rotates in the direction of rotation indicated by the arrow P 2 .
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 la der Nockenwelle 1 eingesetzt werden.The first part 6 and the second part 8 are assembled on the camshaft 1 by pushing them onto the driving surfaces 9 from different sides. If the cam 4 is pressed against the force of the elastic element 14 into the lifting position shown in FIG. 3, the pins 16 can be inserted through the radial grooves in the direction of the axis la of the camshaft 1.
Der Vorteil des variablen Ventiltriebes 2 ist, dass durch die externe Betätigung mittels des Versteilgliedes 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 the external actuation by means of the adjusting member 5 enables a large number of possible variations. 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 patent claims submitted with the application are proposals for formulation without prejudice for the achievement of further patent protection. The applicant reserves the right to claim further features previously only disclosed 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.References used in the subclaims indicate the further development of the subject matter of the skin claim through the features of the respective subclaim; they are not to be understood as a waiver of the achievement of independent, objective protection for the characteristics of the related subclaims.
Die Gegenstände dieser Unteransprüche bilden jedoch auch selbständige Erfindungen, die eine von den Gegenständen der vorhergehenden Unteransprüche unabhängige Gestaltung aufweisen. 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. However, the subjects of these subclaims also form independent inventions which have a design which is independent of the subjects of the preceding subclaims. The invention is also not restricted to the exemplary embodiment (s) of the description. Rather, numerous changes and modifications are possible within the scope of the invention, in particular such variants, elements and combinations and / or materials, for example by combining or modifying individual ones in conjunction with the embodiments described in the general description and the claims and in the drawings Features or elements or process steps contained therein are inventive and, by means of combinable features, lead to a new object or to new process steps or process step sequences, also insofar as they relate to manufacturing, testing and working processes.

Claims

P A T E N T A N S P R Ü C H E PATENT CLAIMS
1. 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 aufweist, dadurch gekennzeichnet, dass der Nocken durch ein seitlich der Nockenwelle angeordnetes Verstellglied ansteuerbar ist.1. Internal combustion engine with a variable valve drive device with at least one camshaft with at least one cam arrangement, which has a cam radially displaceable with respect to the camshaft and at least one, preferably two camshaft-fixed base circle disks, characterized in that the cam can be actuated by an adjusting element arranged on the side of the camshaft is.
2. Brennkraftmaschine, insbesondere nach Anspruch 1, dadurch gekennzeichnet, dass der Nocken jeweils vor oder während einer Hubphase vom Verstellglied von einer Ruheposition in eine Hubposition steuerbar ist.2. Internal combustion engine, in particular according to claim 1, characterized in that the cam can be controlled by the adjusting member from a rest position into a lifting position before or during a lifting phase.
3. Brennkraftmaschine, insbesondere nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der auf der Nockenwelle im Wesentlichen radial verschiebbare Nocken entgegen der Hubposition über ein federndes Element bezüglich der Nockenwelle abgestützt ist und nach der Hubphase von diesem federnden Element in seine Ruhestellung zurückschiebbar ist, wobei vorzugsweise der Nocken sich in der Ruhestellung innerhalb des Grundkreises der Grundkreisscheibe befindet.3. Internal combustion engine, in particular according to claim 1 or 2, characterized in that the cam, which is substantially radially displaceable on the camshaft, is supported against the lifting position by means of a resilient element with respect to the camshaft and can be pushed back into its rest position by this resilient element after the lifting phase, wherein the cam is preferably in the rest position within the base circle of the base disk.
4. Brennkraftmaschine, insbesondere nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Nocken über Gleitflächen auf kreisförmigen Mitnahmeflächen der Nockenwelle gelagert ist.4. Internal combustion engine, in particular according to one of claims 1 to 3, characterized in that the cam is mounted on sliding surfaces on circular driving surfaces of the camshaft.
5. Brennkraftmaschine, insbesondere nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, 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.5. Internal combustion engine, in particular according to one of claims 1 to 4, characterized in that the cam is designed in two parts, wherein a first part acted upon by the adjusting member is viewed in a side view, is essentially fork-shaped and encloses a second part having a cam elevation, wherein first and second parts are preferably connected to one another via pins.
6. Brennkraftmaschine, insbesondere nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Verstellglied zumindest eine Angriffsfläche aufweist, welche mit einer entsprechenden korrespondierenden Gegenfläche des ersten Teiles des Nockens zusammenwirkt.6. Internal combustion engine, in particular according to one of claims 1 to 5, characterized in that the adjusting member has at least one engagement surface which cooperates with a corresponding corresponding counter surface of the first part of the cam.
7. Brennkraftmaschine, insbesondere nach Anspruch 6, dadurch gekennzeichnet, dass 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. 7. Internal combustion engine, in particular according to claim 6, characterized in that the adjusting member has a substantially U-shaped cross section with two legs forming the contact surfaces, which are arranged at a distance from one another which is greater than the width of the second part of the cam ,
8. Brennkraftmaschine, insbesondere nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass das Verstellglied durch eine Betätigungsrolle gebildet ist, wobei die Betätigungsrolle zumindest einen flanschartigen Rand aufweist, dessen Mantelfläche die Angriffsfläche ausbildet.8. Internal combustion engine, in particular according to claim 6 or 7, characterized in that the adjusting member is formed by an actuating roller, the actuating roller having at least one flange-like edge, the outer surface of which forms the engagement surface.
9. Brennkraftmaschine, insbesondere nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, dass 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.9. Internal combustion engine, in particular according to one of claims 5 to 8, characterized in that at least one base circular disc has a radial recess for mounting a pin, wherein recesses of one base circular disc are preferably offset from the recesses of the other base circular disc.
10. Brennkraftmaschine, insbesondere nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass zumindest eine Grundkreisscheibe eine Rampenerhebung aufweist, welche gemeinsam mit der Nockenerhebung des zweiten Teiles des Nockens die Ventilhubkurve für zumindest ein Gaswechselventil definiert.10. Internal combustion engine, in particular according to one of claims 1 to 9, characterized in that at least one base plate has a ramp elevation, which defines the valve lift curve for at least one gas exchange valve together with the cam elevation of the second part of the cam.
11. Brennkraftmaschine, insbesondere nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Gegenfläche des ersten Teiles eine von einer Zylinderfläche abweichende Form aufweist und eine Steuerkurve definiert, so dass die Ventilhubkurve des zu betätigenden Gaswechselventils sich aus der Form der Steuerkurve des ersten Teiles und der Form der Nockenerhebung des zweiten Teiles des Nockens zusammensetzt.11. Internal combustion engine, in particular according to one of claims 1 to 9, characterized in that the counter surface of the first part has a shape deviating from a cylinder surface and defines a control curve, so that the valve lift curve of the gas exchange valve to be actuated is derived from the shape of the control curve of the first Part and the shape of the cam elevation of the second part of the cam is composed.
12. Brennkraftmaschine, insbesondere nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die Steuerkurve 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.12. Internal combustion engine, in particular according to one of claims 1 to 10, characterized in that the control curve and the cam elevation of the cam are shaped such that the valve lift curve runs continuously, in particular in the region of the transition between the base circle of the base circle disks for cam elevation of the cam.
13. Verfahren zum Betreiben einer Brennkraftmaschine, insbesondere einer Die- sel-Brennkraftmaschine, mit vollvariablem Ventiltrieb, dadurch gekennzeichnet, dass während der Startphase und/oder während Betriebsphasen mit niedrigem Verdichtungsverhältnis der Einlassventilöffnungszeitpunkt nach spät und/oder der Einlassschließzeitpunkt nach früh verstellt wird. 13. Method for operating an internal combustion engine, in particular a diesel internal combustion engine, with a fully variable valve train, characterized in that during the starting phase and / or during operating phases with a low compression ratio, the intake valve opening time is adjusted late and / or the intake closing time is adjusted early.
EP04737352A 2003-06-24 2004-06-24 Internal combustion engine Expired - Lifetime EP1636466B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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

Publications (2)

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

Family

ID=29588081

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04737352A Expired - Lifetime EP1636466B1 (en) 2003-06-24 2004-06-24 Internal combustion engine

Country Status (6)

Country Link
US (1) US7424877B2 (en)
EP (1) EP1636466B1 (en)
CN (1) CN100443696C (en)
AT (2) AT6651U1 (en)
DE (1) DE502004007682D1 (en)
WO (1) WO2004113688A2 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007010149A1 (en) * 2007-03-02 2008-09-04 Audi Ag Automotive piston engine gas valve timer has right- and left-handed grooves are located immediately alongside and translating into each other
JP5069958B2 (en) * 2007-07-03 2012-11-07 株式会社オティックス Rocker arm
AT510527B1 (en) * 2010-09-23 2012-09-15 Avl List Gmbh FOUR-STROKE COMBUSTION ENGINE WITH A MOTOR BRAKE
JP5488512B2 (en) * 2011-03-28 2014-05-14 三菱自動車工業株式会社 Cam structure

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2448032A1 (en) * 1979-02-05 1980-08-29 Semt PROCESS FOR IMPROVING THE EFFICIENCY OF AN INTERNAL COMBUSTION ENGINE, ESPECIALLY SUPERCHARGED
US4805571A (en) * 1985-05-15 1989-02-21 Humphrey Cycle Engine Partners, L.P. Internal combustion engine
DE3737824A1 (en) 1987-11-06 1989-05-18 Schatz Oskar Method for operating an internal combustion engine of the piston type
JPH01178710A (en) 1988-01-06 1989-07-14 Mazda Motor Corp Valve driving device for engine
US5136887A (en) 1990-05-29 1992-08-11 Clemson University Variable valve actuating apparatus
US5404770A (en) * 1991-08-14 1995-04-11 Volkswagen Ag Variable cam arrangement for a lift valve
DE4222477A1 (en) 1991-08-14 1993-02-18 Volkswagen Ag Cam mechanism for IC engine valve - has radially adjustable cam component to adjust amount of valve lift obtained
DE4141482A1 (en) 1991-12-16 1993-06-17 Schatz Oskar METHOD FOR AIR INLET INTO THE COMBUSTION CHAMBER OF A PISTON-COMBUSTION ENGINE IN TWO PHASES
EP0705382B1 (en) * 1994-03-03 1998-07-15 Christos Valasopoulos Variable action arrowhead shaped cam lobe system
US5813377A (en) * 1995-11-07 1998-09-29 Yamaha Hatsudoki Kabushiki Kaisha Engine valve operating system
US6279550B1 (en) * 1996-07-17 2001-08-28 Clyde C. Bryant Internal combustion engine
JP3257480B2 (en) 1997-10-09 2002-02-18 トヨタ自動車株式会社 Starting device and starting method for internal combustion engine
JP4394764B2 (en) * 1999-02-15 2010-01-06 日立オートモティブシステムズ株式会社 Variable valve operating device for internal combustion engine
DE19908435A1 (en) 1999-02-26 2000-09-07 Meta Motoren Energietech Method and device for pulse charging a piston internal combustion engine
US6427653B1 (en) 1999-10-29 2002-08-06 Unisia Jecs Corporation System for driving and controlling CAM for internal combustion engine
DE10030904A1 (en) * 2000-06-23 2002-01-31 Audi Ag Variable geometry camshaft for IC engine has radially adjustable cam segment to vary valve stroke
DE10101011A1 (en) * 2001-01-11 2002-07-18 Volkswagen Ag Camshaft with radially adjustable cam profile for variable lift of lifting elements has control shaft adjustment with cam mounted within camshaft that engages radially deployable cam profile
DE10217695A1 (en) 2002-04-20 2003-11-13 Daimler Chrysler Ag Starting method for IC engine using adjustment of closure timing of engine intake valves and selective closure of intake channel for each engine cylinder

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004113688A2 *

Also Published As

Publication number Publication date
WO2004113688A2 (en) 2004-12-29
US20060169235A1 (en) 2006-08-03
DE502004007682D1 (en) 2008-09-04
AT6651U1 (en) 2004-01-26
US7424877B2 (en) 2008-09-16
CN1839249A (en) 2006-09-27
CN100443696C (en) 2008-12-17
ATE402327T1 (en) 2008-08-15
WO2004113688A3 (en) 2005-06-09
EP1636466B1 (en) 2008-07-23

Similar Documents

Publication Publication Date Title
AT408127B (en) Internal combustion engine with at least one camshaft that can be axially displaced by an adjusting device
EP2132418B1 (en) Valve drive for gas exchange valves of an internal combustion engine, comprising a movable cam support and a twin worm gear
EP2702253B1 (en) Valve drive for gas exchange valves of an internal combustion engine having a main camshaft and cam carriers which can be displaced between rotary bearings of the main camshaft into two or more discrete displacement positions
DE102016204893A1 (en) Valve train for an internal combustion engine
WO2014019684A1 (en) Actuating unit for variable power plant components
DE102007010156A1 (en) Valve drive unit for a combustion engine comprises an adjusting unit having interacting elements which interact alternately with a curved connecting part
DE102007002802A1 (en) Valve train changing method for internal combustion engine, involves shifting cam carrier between axial position, which is assigned to two stroke operation, and another axial position, which is assigned to four-stroke operation
DE102007010155A1 (en) Camshaft for IC engine has two cam followers plus a circular cam which slides axially into the cam bearing for the non operating valve setting
DE102012002026A1 (en) Variable-stroke valve drive for internal combustion engine, has eccentric shaft with eccentric cams having angular range, in which stroke of valve and of similar valve group vary differently from each other
EP3222828A2 (en) Valve drive for an internal combustion engine
WO2005075797A1 (en) Drag lever for deviation switching
WO2017025477A1 (en) Valve train for an internal combustion engine
EP0521412A1 (en) Internal combustion engine with rocker lever valve drive
DE102011085706A1 (en) Valve train for multi-cylinder combustion engine of motorcycle, has position unit whose actuator pins radially extend to cam shaft, where outer jacket surface of portion of actuator pins engage at guide surfaces
DE19540133C2 (en) Valve lifter
DE10105807C1 (en) Pivot lever for operation of internal combustion engine valve has mechanical valve play setting element using rotatable hollow cylinder with planar surfaces for operation of valve shaft
AT517816B1 (en) VARIABLE VALVE CONTROL DEVICE FOR INTERNAL COMBUSTION ENGINES
EP3441581B1 (en) Sliding cam system and method for operating a combustion engine
EP1636466B1 (en) Internal combustion engine
WO2017076482A1 (en) Valve train device
EP3173593B1 (en) Variable valve drive with a rocker arm
EP1619362A2 (en) Valve train for an internal combustion engine
WO2022112525A1 (en) Sliding-cam camshaft arrangement for an internal combustion engine, and method for switching a sliding-cam camshaft arrangement for an internal combustion engine
DE102007031815A1 (en) Valve gear for internal combustion engine, has control unit adjusting roller and formed at cam arrangement of cam shaft, where roller is admittable with different cam contours by control unit based on switched-rolling position of roller
WO1995028556A1 (en) Pull-rod for actuating a gas changeover valve

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20051205

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20060829

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502004007682

Country of ref document: DE

Date of ref document: 20080904

Kind code of ref document: P

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081223

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081023

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

BERE Be: lapsed

Owner name: AVL LIST GMBH

Effective date: 20090630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081023

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090624

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100226

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090624

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090624

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081024

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090624

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090124

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080723

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180831

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004007682

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200101