EP2464833B1 - Valve train for internal combustion engines for actuating gas exchange valves - Google Patents

Valve train for internal combustion engines for actuating gas exchange valves Download PDF

Info

Publication number
EP2464833B1
EP2464833B1 EP10760229.4A EP10760229A EP2464833B1 EP 2464833 B1 EP2464833 B1 EP 2464833B1 EP 10760229 A EP10760229 A EP 10760229A EP 2464833 B1 EP2464833 B1 EP 2464833B1
Authority
EP
European Patent Office
Prior art keywords
cam
switching
sleeves
valve train
sleeve
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.)
Not-in-force
Application number
EP10760229.4A
Other languages
German (de)
French (fr)
Other versions
EP2464833A2 (en
Inventor
Andreas Werler
Thomas Arnold
Heiko Neukirchner
Jörg Wutzler
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.)
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Original Assignee
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
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 IAV GmbH Ingenieurgesellschaft Auto und Verkehr filed Critical IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Publication of EP2464833A2 publication Critical patent/EP2464833A2/en
Application granted granted Critical
Publication of EP2464833B1 publication Critical patent/EP2464833B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0042—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams being profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve
    • 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 a valve train for internal combustion engines for actuating gas exchange valves with the features mentioned in the preamble of claim 1.
  • the disadvantage here is the high space requirement, which is needed to adjust the cam carrier. These solutions are therefore only applicable at relatively large cylinder spacings to accommodate the corresponding components can. Another disadvantage is the high mass forces that occur during the adjustment process, which are needed to move the cam carrier or the adjusting organs. Switching over to a corresponding cam contour can only be done in a cylinder-selective manner. Valve-selective switching is not possible.
  • the DE 100 54 623 A1 describes a device for switching a cam carrier on a camshaft for actuating gas exchange valves, in which the cam carrier is guided axially displaceably on the camshaft. According to the position of the cam carrier, the gas exchange valve is in operative connection with different cam contours.
  • the control element is a radially outwardly displaceable pin, which is connected to at least two in a by about 180 ° around the cam carrier arranged around guide part formed link tracks in the extended state cooperates.
  • a disadvantage of this solution in addition to the additional space for the guide member is that extended to switch to another cam contour of the pin from the camshaft and must be meshed in an axially displaceable shift gate. After switching, the pin must be retracted. This design is very part and production-consuming and there is a risk of damage to the camshaft by faulty circuits of the pin.
  • Another disadvantage is that the motor speed is limited by the necessary actuating time of the pin. In addition, the adjustment depends on the existing oil pressure.
  • the disadvantage of this solution is that only a plurality of cam carriers arranged on the cam carrier can be moved simultaneously by the axial displacement of the adjusting. A different circuit of individual cam carriers on a camshaft is not possible.
  • Another disadvantage is that at a switching position in which an outer cam is engaged with the gas exchange valves, the spring element is constantly stretched. As a result, high lateral frictional forces occur between the driving piece and the guideway arranged on the adjusting member. An increased wear and associated possible faulty circuits are the result.
  • a further disadvantage is that the acting spring forces must be set accurately to faulty circuits, in particular when switching back to the central cam profile with three different cam profiles, to avoid.
  • valve train for actuating gas exchange valves of internal combustion engines.
  • the displacement of the cam carrier for valve switching on the camshaft tube is effected by a rotatable switching shaft arranged in the interior of the camshaft tube.
  • the switching shaft is provided with a switching contour having an axial slope.
  • a switching ball is guided, which is mounted in a bore of a switching shaft surrounding the axially displaceable shift sleeve.
  • the switching sleeve is connected via a driver with the cam carrier in operative connection.
  • the invention has for its object to provide a valve train for actuating gas exchange valves of internal combustion engines, which is characterized by a simplified structure while reducing the friction forces occurring.
  • the valve drive according to the invention for internal combustion engines for actuating gas exchange valves consists of a driven by a crankshaft of the internal combustion engine camshaft, which is formed of a plurality of individual mutually axially displaceable cam sleeves.
  • On each cam sleeve several different cam profiles are arranged with the same base circle section, which can be brought by displacement of the individual cam sleeves with the gas exchange valves engaged.
  • a co-rotating with the cam sleeves switching shaft is arranged, which are in each case via a switching pin with the respective cam sleeve in operative connection.
  • each cam sleeve At the inner periphery of each cam sleeve, a circumferential switching contour is arranged, in which the driver is slidably mounted.
  • the switching shaft is connected to an actuator with which a relative rotation of the switching shaft relative to the cam sleeves is triggered during a switching operation for moving the cam sleeves.
  • the advantage of the solution according to the invention consists in a simple design of the actuator for safe valve switching between different cam profiles of the camshaft at the same time the friction occurring between the individual components has been reduced.
  • valve drive for actuating gas exchange valves consists of a driven by a crankshaft of the internal combustion engine camshaft, which is formed of a plurality of individual mutually axially displaceable cam sleeves 7.
  • Each cylinder of a multi-cylinder internal combustion engine is associated with an axially displaceable cam sleeve 7, with which, according to the embodiment, two gas exchange valves of a cylinder can be actuated by the two cam profiles 9 arranged on the cam sleeve 7.
  • the cam sleeve 7 has at a same base circle portion 10 a plurality of differently shaped cam profiles 9a, 9b and 9c, which are brought to Ventilhubumsciens either by moving the cam sleeve 7 respectively directly or via non-illustrated intermediate members with a respective gas exchange valve in contact.
  • each has Cam sleeve 7 two cam profiles 9, each with a small cam profile 9a, a central cam profile 9b and a large cam profile 9c for actuating the two gas exchange valves, on.
  • the cam profiles 9 of each cam sleeve 7 are formed from only two or more than three different sized cam profiles.
  • the curves of the cam profiles 9a, 9b and 9c can be arranged offset to one another.
  • the individual mutually axially displaceable cam sleeves 7 are connected to each other by an axially extending toothing 8.
  • the cam sleeves 7 are formed such that the toothing 8 of the respectively adjacent cam sleeves 7 are formed engaging one another. This ensures that the individual cam sleeves 7 are mutually axially displaceable and rotatably connected to each other.
  • a switching shaft 1 is arranged, which, except during the switching process, rotates synchronously with the cam sleeves 7.
  • Each cam sleeve 7 is connected via a switching pin 3 with the switching shaft 1 in operative connection.
  • the shift pin 3 is fixedly connected to the shift shaft 1 and slidably mounted in a circumferentially arranged on the inner circumference of the cam sleeves 7 switching contour 2.
  • the arranged on the inner circumference of the cam sleeves 7 circumferential switching contour 2 has a plurality of different axial slopes.
  • the individual axial slopes of the arranged for each cam sleeve 7 switching contour 2 on the inner circumference of the cam sleeves 7 are arranged offset from one another.
  • the individual axial slopes of the switching contour 2 arranged for each cam sleeve 7 lie on the inner circumference of the cam sleeves 7 in the same axial plane.
  • the switching shaft 1 is connected to one with an actuator 6 for generating a relative rotation of the switching shaft 1 relative to the cam sleeves 7 in operative connection.
  • the actuator 6 may be connected directly or as shown in the drawing via a cam gear with the shift shaft 1.
  • the cam mechanism consists of a arranged on the circumference of the switching shaft 1 switching contour 13 in the sliding a switching ball 4 is mounted, which in turn is mounted in a arranged on the inner circumference of a sliding piece 5 hemispherical receptacle.
  • the sliding piece 5 is rotatably but axially displaceably connected to a cam sleeve 7. The connection between the cam sleeve 7 and sliding piece 5 takes place via an intermeshing axial toothing.
  • the sliding piece 5 can be brought into operative connection with a housing of the internal combustion engine firmly connected actuator 6.
  • a pin 11 arranged on the actuator 6 engages in the contour 12 arranged on the circumference of the displacement piece 5.
  • the sliding piece 5 is axially displaceable relative to a cam sleeve 7 in both directions according to the double arrow shown in the drawing.
  • variable valve train for realizing a changeover between the different cam profiles 9a, 9b and 9c is as follows.
  • the central cam profiles 9b of the cam sleeve 7 with the gas exchange valves, the cam sleeves 7, the switching shaft 1 and the sliding piece 5 rotate at a synchronous speed.
  • the actuator 6 is not engaged with the sliding piece 5.
  • a changeover to another cam profile can only be performed when the base circle portion 10 is in engagement with the gas exchange valve or the intermediate member.
  • the actuator 6 is activated by a corresponding control and brought into engagement with the sliding piece 5. In the described embodiment, this takes place in that a pin 11 is extended in the direction of the sliding piece 5 and engages in the contour 12 arranged on the circumference of the sliding piece 5.
  • the sliding piece 5 is axially displaced relative to the cam sleeve 7 by the pin 11 sliding in the contour 12 to the right or to the left, according to the switching operation to be carried out.
  • the axial movement of the sliding piece 5 is translated into a rotation of the shift shaft 1.
  • Due to the relative rotation of the hemispherical formed part of the switching pin 3 slides in the path of the rotating switching contour 2 of the cam sleeve 7.
  • According to the realized relative rotation and the execution of the individual with each cam sleeve 7 via the switching balls 3 operatively connected switching contours 2 takes place an axial displacement of the cam sleeves 7 against each other and thus switching between the individual cam profiles 9a, 9b and 9c.
  • the displacement of the sliding piece 5 can also be effected, for example, by an actuator 6 that acts magnetically on the sliding piece 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

Die Erfindung betrifft einen Ventiltrieb für Verbrennungskraftmaschinen zur Betätigung von Gaswechselventilen mit den im Oberbegriff des Patentanspruches 1 genannten Merkmalen.The invention relates to a valve train for internal combustion engines for actuating gas exchange valves with the features mentioned in the preamble of claim 1.

Es ist bekannt, Gaswechselventile einer Brennkraftmaschine variabel mit unterschiedlichen Öffnungs- und Schließzeitpunkten sowie mit unterschiedlichen Ventilöffnungshüben zu betreiben. Eine derartige Ventilsteuerung ist aus der DE 42 30 877 A1 vorbekannt. Dabei ist auf einer Nockenwelle drehfest, aber axial verschiebbar ein Nockenträger mit zwei unterschiedlichen Nockenkonturen angeordnet. Entsprechend der Axialstellung des Nockenträgers steht eine Nockenkontur über ein Zwischenglied (Übertragungshebel) mit dem Hubventil in Wirkverbindung. Die Axialverschiebung des Nockenträgers zur Änderung der Ventilparameter erfolgt während der Grundkreisphase entgegen der Wirkung einer Rückstellfeder mittels eines Druckringes.It is known to operate gas exchange valves of an internal combustion engine variable with different opening and closing times and with different valve opening strokes. Such a valve control is from the DE 42 30 877 A1 previously known. In this case, a cam carrier with two different cam contours is arranged rotatably on a camshaft, but axially displaceable. According to the axial position of the cam carrier is a cam contour via an intermediate member (transmission lever) with the globe valve in operative connection. The axial displacement of the cam carrier to change the valve parameters takes place during the base circle phase against the action of a return spring by means of a pressure ring.

Nachteilig ist dabei der hohe Bauraumbedarf, der zur Verstellung des Nockenträgers benötigt wird. Diese Lösungen sind deshalb nur einsetzbar bei verhältnismäßig großen Zylinderabständen, um die entsprechenden Bauteile unterbringen zu können. Ein weiterer Nachteil sind die beim Stellvorgang auftretenden hohen Massenkräfte, die zum Verschieben der Nockenträger oder der Verstellorgane benötigt werden. Die Umschaltung auf eine entsprechende Nockenkontur kann nur zylinderselektiv erfolgen. Eine ventilselektive Umschaltung ist nicht möglich.The disadvantage here is the high space requirement, which is needed to adjust the cam carrier. These solutions are therefore only applicable at relatively large cylinder spacings to accommodate the corresponding components can. Another disadvantage is the high mass forces that occur during the adjustment process, which are needed to move the cam carrier or the adjusting organs. Switching over to a corresponding cam contour can only be done in a cylinder-selective manner. Valve-selective switching is not possible.

Die DE 100 54 623 A1 beschreibt eine Vorrichtung zum Umschalten eines Nockenträgers auf einer Nockenwelle zur Betätigung von Gaswechselventilen, bei der der Nockenträger axial verschiebbar auf der Nockenwelle geführt ist. Entsprechend der Position des Nockenträgers steht das Gaswechselventil mit unterschiedlichen Nockenkonturen in Wirkverbindung. Die Verstellung des Nockenträgers erfolgt über ein Stellelement im Zusammenwirken mit einer Kulissenbahn. Das Stellelement ist dabei ein radial nach außen verschiebbarer Pin, der mit zumindest zwei in einem um ca. 180° um den Nockenträger herum angeordneten Führungsteil ausgebildeten Kulissenbahnen im ausgefahrenen Zustand zusammenwirkt.The DE 100 54 623 A1 describes a device for switching a cam carrier on a camshaft for actuating gas exchange valves, in which the cam carrier is guided axially displaceably on the camshaft. According to the position of the cam carrier, the gas exchange valve is in operative connection with different cam contours. The adjustment of the cam carrier via an actuator in cooperation with a slide track. The control element is a radially outwardly displaceable pin, which is connected to at least two in a by about 180 ° around the cam carrier arranged around guide part formed link tracks in the extended state cooperates.

Ein Nachteil dieser Lösung besteht neben dem zusätzlichen Bauraum für das Führungsteil darin, dass zum Umschalten auf eine andere Nockenkontur der Pin aus der Nockenwelle ausgefahren und in eine axial verschiebbare Schaltkulisse eingespurt werden muss. Nach dem Schaltvorgang muss der Pin wieder eingefahren werden. Diese Konstruktion ist sehr teile- und fertigungsaufwendig und es besteht die Gefahr von Schäden an der Nockenwelle durch Fehlschaltungen des Pins. Ein weiterer Nachteil besteht darin, dass durch die notwendige Stellzeit des Pins die Motordrehzahl begrenzt wird. Außerdem ist die Verstellung abhängig von dem jeweils vorhandenen Öldruck.A disadvantage of this solution, in addition to the additional space for the guide member is that extended to switch to another cam contour of the pin from the camshaft and must be meshed in an axially displaceable shift gate. After switching, the pin must be retracted. This design is very part and production-consuming and there is a risk of damage to the camshaft by faulty circuits of the pin. Another disadvantage is that the motor speed is limited by the necessary actuating time of the pin. In addition, the adjustment depends on the existing oil pressure.

Weiterhin ist aus der DE 195 20 117 C2 ein Ventiltrieb einer Brennkraftmaschine vorbekannt, bei dem auf der Nockenwelle drehfest ein axial verschiebbarer Nockenträger mit mindestens zwei unterschiedlichen Nockenbahnen angeordnet ist. Die Verstellung des Nockenträgers erfolgt über ein Verstellorgan, das im Inneren der Nockenwelle geführt ist. Durch eine stirnseitig an der Nockenwelle angeordnete doppelt wirkende hydraulische oder pneumatische Kolben-Zylinder-Einheit wird das wellenartig ausgebildete Verstellorgan im Inneren der Nockenwelle gegen den Druck einer Feder verschoben. Das Verstellorgan ist mit einem Mitnahmestück verbunden, das ein axial in der Nockenwelle angeordnetes Langloch durchdringt und in eine Bohrung des Nockenträgers mündet.Furthermore, from the DE 195 20 117 C2 a valve train of an internal combustion engine previously known, in which on the camshaft rotationally fixed an axially displaceable cam carrier is arranged with at least two different cam tracks. The adjustment of the cam carrier via an adjusting member which is guided inside the camshaft. By a frontally arranged on the camshaft double-acting hydraulic or pneumatic piston-cylinder unit, the wave-like adjusting member is moved in the interior of the camshaft against the pressure of a spring. The adjusting member is connected to a driving piece, which penetrates an axially arranged in the camshaft slot and opens into a bore of the cam carrier.

Der Nachteil dieser Lösung besteht darin, dass durch die axiale Verschiebung des Verstellorgans nur mehrere auf der Nockenwelle angeordnete Nockenträger gleichzeitig verschoben werden können. Eine unterschiedliche Schaltung von einzelnen Nockenträgern auf einer Nockenwelle ist nicht möglich. Ein weiterer Nachteil besteht darin, dass bei einer Schaltposition, bei der ein äußerer Nocken im Eingriff mit den Gaswechselventilen steht, das Federelement ständig gespannt ist. Dadurch treten hohe seitliche Reibkräfte zwischen dem Mitnehmerstück und der auf dem Verstellorgan angeordneten Führungsbahn auf. Ein erhöhter Verschleiß und damit verbundene eventuelle Fehlschaltungen sind die Folge. Nachteilig ist weiterhin, dass die wirkenden Federkräfte genau eingestellt werden müssen, um Fehlschaltungen, insbesondere bei Rückschaltung auf das mittlere Nockenprofil bei drei unterschiedlichen Nockenprofilen, zu vermeiden.The disadvantage of this solution is that only a plurality of cam carriers arranged on the cam carrier can be moved simultaneously by the axial displacement of the adjusting. A different circuit of individual cam carriers on a camshaft is not possible. Another disadvantage is that at a switching position in which an outer cam is engaged with the gas exchange valves, the spring element is constantly stretched. As a result, high lateral frictional forces occur between the driving piece and the guideway arranged on the adjusting member. An increased wear and associated possible faulty circuits are the result. A further disadvantage is that the acting spring forces must be set accurately to faulty circuits, in particular when switching back to the central cam profile with three different cam profiles, to avoid.

Durch die DE 10 2009 017 242 der Anmelderin wurde bereits ein Ventiltriebs zur Betätigung von Gaswechselventilen von Brennkraftmaschinen vorgeschlagen. Bei dem Ventiltrieb erfolgt die Verschiebung des Nockenträgers zur Ventilumschaltung auf dem Nockenwellenrohr durch eine im Inneren des Nockenwellenrohrs angeordnete verdrehbare Schaltwelle. Die Schaltwelle ist mit einer Schaltkontur versehen, die eine axiale Steigung aufweist. In der Schaltkontur wird eine Schaltkugel geführt, die in einer Bohrung einer die Schaltwelle umgebenden axial verschiebbaren Schalthülse gelagert ist. Die Schalthülse steht über einen Mitnehmer mit dem Nockenträger in Wirkverbindung. Durch Verdrehen der Schaltwelle wird über die Schaltkugel die Schalthülse und über den Mitnehmer der Nockenträger axial verschoben.By the DE 10 2009 017 242 the applicant has already proposed a valve train for actuating gas exchange valves of internal combustion engines. In the case of the valve drive, the displacement of the cam carrier for valve switching on the camshaft tube is effected by a rotatable switching shaft arranged in the interior of the camshaft tube. The switching shaft is provided with a switching contour having an axial slope. In the switching contour, a switching ball is guided, which is mounted in a bore of a switching shaft surrounding the axially displaceable shift sleeve. The switching sleeve is connected via a driver with the cam carrier in operative connection. By turning the selector shaft, the shift sleeve and the driver of the cam carrier is axially displaced via the switching ball.

Durch die Anordnung einer Schalthülse zwischen der Schaltwelle und dem Nockenwellenrohr treten zusätzlich zu überwindende Reibungskräfte auf. Außerdem ist die Lösung durch die Anordnung der Schalthülse sehr teileaufwändig.By arranging a shift sleeve between the shift shaft and the camshaft tube occur in addition to overcoming friction forces. In addition, the solution is very expensive due to the arrangement of the switching sleeve.

Der Erfindung liegt die Aufgabe zugrunde, einen Ventiltrieb zur Betätigung von Gaswechselventilen von Verbrennungskraftmaschinen zu schaffen, der sich durch einen vereinfachten Aufbau bei gleichzeitiger Reduzierung der auftretenden Reibungskräfte auszeichnet.The invention has for its object to provide a valve train for actuating gas exchange valves of internal combustion engines, which is characterized by a simplified structure while reducing the friction forces occurring.

Erfindungsgemäß wird die Aufgabe durch die Merkmale des Patentanspruches 1 gelöst.According to the invention the object is achieved by the features of claim 1.

Der erfindungsgemäße Ventiltrieb für Verbrennungskraftmaschinen zur Betätigung von Gaswechselventilen besteht aus einer von einer Kurbelwelle der Verbrennungskraftmaschine angetriebenen Nockenwelle, die aus mehreren einzelnen gegeneinander axial verschiebbaren Nockenhülsen gebildet wird. Die Verbindung der einzelnen separat gegeneinander verschiebbaren Nockenhülsen miteinander erfolgt über eine axial verlaufende Verzahnung, wobei die Verzahnungen der jeweils benachbarten Nockenhülsen ineinander eingreifend ausgebildet sind. Auf jeder Nockenhülse sind mehrere unterschiedliche Nockenprofile mit gleichem Grundkreisabschnitt angeordnet, die durch Verschiebung der einzelnen Nockenhülsen mit den Gaswechselventilen in Eingriff gebracht werden können. Im Inneren der Nockenhülsen ist eine sich mit den Nockenhülsen mitdrehende Schaltwelle angeordnet, die jeweils über einen Schaltpin mit der jeweiligen Nockenhülse in Wirkverbindung stehen. Am inneren Umfang jeder Nockenhülse ist eine umlaufende Schaltkontur angeordnet, in der der Mitnehmer gleitend gelagert ist. Die Schaltwelle ist mit einem Aktuator verbunden, mit dem während eines Schaltvorganges zum Verschieben der Nockenhülsen eine Relativverdrehung der Schaltwelle gegenüber den Nockenhülsen ausgelöst wird.The valve drive according to the invention for internal combustion engines for actuating gas exchange valves consists of a driven by a crankshaft of the internal combustion engine camshaft, which is formed of a plurality of individual mutually axially displaceable cam sleeves. The connection of the individual mutually displaceable cam sleeves with each other via an axially extending teeth, wherein the teeth of the respective adjacent cam sleeves are formed engaging one another. On each cam sleeve several different cam profiles are arranged with the same base circle section, which can be brought by displacement of the individual cam sleeves with the gas exchange valves engaged. In the interior of the cam sleeves a co-rotating with the cam sleeves switching shaft is arranged, which are in each case via a switching pin with the respective cam sleeve in operative connection. At the inner periphery of each cam sleeve, a circumferential switching contour is arranged, in which the driver is slidably mounted. The switching shaft is connected to an actuator with which a relative rotation of the switching shaft relative to the cam sleeves is triggered during a switching operation for moving the cam sleeves.

Der Vorteil der erfindungsgemäßen Lösung besteht in einem einfachen Aufbau der Betätigungsvorrichtung zur sicheren Ventilumschaltung zwischen unterschiedlichen Nockenprofilen der Nockenwelle bei der gleichzeitig die zwischen den einzelnen Bauteilen auftretende Reibung reduziert wurde.The advantage of the solution according to the invention consists in a simple design of the actuator for safe valve switching between different cam profiles of the camshaft at the same time the friction occurring between the individual components has been reduced.

Weitere vorteilhafte Ausgestaltungen sind in den Unteransprüchen beschrieben, sie werden in der Beschreibung zusammen mit ihren Wirkungen erläutert.Further advantageous embodiments are described in the subclaims, they are explained in the description together with their effects.

Anhand einer Zeichnung, die eine Schnittdarstellung der erfindungsgemäßen Lösung zeigt, wird die Erfindung nachfolgend an Ausführungsbeispielen näher beschrieben.Reference to a drawing showing a sectional view of the solution according to the invention, the invention will be described in more detail below by exemplary embodiments.

In der Zeichnung ist ein Teilbereich eines Ventiltriebs einer Brennkraftmaschine dargestellt. Der Ventiltrieb zur Betätigung von nicht dargestellten Gaswechselventilen besteht aus einer von einer Kurbelwelle der Verbrennungskraftmaschine angetriebenen Nockenwelle, die aus mehreren einzelnen gegeneinander axial verschiebbaren Nockenhülsen 7 gebildet wird. Jedem Zylinder einer mehrzylindrigen Brennkraftmaschine ist eine axial verschiebbare Nockenhülse 7 zugeordnet, mit dem, entsprechend dem Ausführungsbeispiel, jeweils zwei Gaswechselventile eines Zylinders durch die beiden auf der Nockenhülse 7 angeordneten Nockenprofile 9 betätigt werden können. Die Nockenhülse 7 weist bei einem gleichen Grundkreisabschnitt 10 mehrere unterschiedlich ausgebildete Nockenprofile 9a, 9b und 9c auf, die zur Ventilhubumschaltung wahlweise durch Verschieben der Nockenhülse 7 jeweils direkt oder über nicht dargestellte Zwischenglieder mit einem jeweiligen Gaswechselventil in Kontakt gebracht werden. In dem dargestellten Ausführungsbeispiel weist jede Nockenhülse 7 zwei Nockenprofile 9, mit jeweils einem kleinen Nockenprofil 9a, einem mittleren Nockenprofil 9b und einem großen Nockenprofil 9c zur Betätigung der beiden Gaswechselventile, auf. Es ist durchaus denkbar, dass die Nockenprofile 9 jeder Nockenhülse 7 aus nur zwei oder mehr als drei unterschiedlich großen Nockenprofilen gebildet werden. Zur Erzielung einer Phasenverschiebung zwischen den unterschiedlichen Nockenprofilen 9a, 9b und 9c können die Kurven der Nockenprofile 9a, 9b und 9c zueinander versetzt angeordnet sein.In the drawing, a portion of a valve train of an internal combustion engine is shown. The valve drive for actuating gas exchange valves, not shown, consists of a driven by a crankshaft of the internal combustion engine camshaft, which is formed of a plurality of individual mutually axially displaceable cam sleeves 7. Each cylinder of a multi-cylinder internal combustion engine is associated with an axially displaceable cam sleeve 7, with which, according to the embodiment, two gas exchange valves of a cylinder can be actuated by the two cam profiles 9 arranged on the cam sleeve 7. The cam sleeve 7 has at a same base circle portion 10 a plurality of differently shaped cam profiles 9a, 9b and 9c, which are brought to Ventilhubumschaltung either by moving the cam sleeve 7 respectively directly or via non-illustrated intermediate members with a respective gas exchange valve in contact. In the illustrated embodiment, each has Cam sleeve 7 two cam profiles 9, each with a small cam profile 9a, a central cam profile 9b and a large cam profile 9c for actuating the two gas exchange valves, on. It is quite conceivable that the cam profiles 9 of each cam sleeve 7 are formed from only two or more than three different sized cam profiles. To achieve a phase shift between the different cam profiles 9a, 9b and 9c, the curves of the cam profiles 9a, 9b and 9c can be arranged offset to one another.

Die einzelnen gegeneinander axial verschiebbaren Nockenhülsen 7 sind miteinander durch eine axial verlaufende Verzahnung 8 verbunden. Dabei sind die Nockenhülsen 7 derart ausgebildet, dass die Verzahnung 8 der jeweils benachbarten Nockenhülsen 7 ineinander eingreifend ausgebildet sind. Dadurch wird erreicht, dass die einzelnen Nockenhülsen 7 gegeneinander axial verschiebbar und drehfest miteinander verbunden sind. Innerhalb der Nockenhülsen 7 ist eine Schaltwelle 1 angeordnet, die sich, außer während des Schaltprozesses, synchron mit den Nockenhülsen 7 mitdreht. Jede Nockenhülse 7 steht über einen Schaltpin 3 mit der Schaltwelle 1 in Wirkverbindung. Der Schaltpin 3 ist fest mit der Schaltwelle 1 verbunden und in einer am Innenumfang der Nockenhülsen 7. angeordneten umlaufenden Schaltkontur 2 gleitend gelagert. Die am Innenumfang der Nockenhülsen 7 angeordnete umlaufende Schaltkontur 2 weist mehrere unterschiedliche axiale Steigungen auf. Bei einer nacheinander durchzuführenden axialen Verschiebung der einzelnen Nockenhülsen 7 sind die einzelnen axialen Steigungen der für jede Nockenhülse 7 angeordneten Schaltkontur 2 am Innenumfang der Nockenhülsen 7 zueinander versetzt angeordnet. Bei einer gleichzeitigen axialen Verschiebung der einzelnen Nockenhülsen 7 liegen die einzelnen axialen Steigungen der für jede Nockenhülse 7 angeordneten Schaltkontur 2 am Innenumfang der Nockenhülsen 7 in gleicher axialer Ebene.The individual mutually axially displaceable cam sleeves 7 are connected to each other by an axially extending toothing 8. In this case, the cam sleeves 7 are formed such that the toothing 8 of the respectively adjacent cam sleeves 7 are formed engaging one another. This ensures that the individual cam sleeves 7 are mutually axially displaceable and rotatably connected to each other. Within the cam sleeves 7, a switching shaft 1 is arranged, which, except during the switching process, rotates synchronously with the cam sleeves 7. Each cam sleeve 7 is connected via a switching pin 3 with the switching shaft 1 in operative connection. The shift pin 3 is fixedly connected to the shift shaft 1 and slidably mounted in a circumferentially arranged on the inner circumference of the cam sleeves 7 switching contour 2. The arranged on the inner circumference of the cam sleeves 7 circumferential switching contour 2 has a plurality of different axial slopes. In a successive axial displacement of the individual cam sleeves 7, the individual axial slopes of the arranged for each cam sleeve 7 switching contour 2 on the inner circumference of the cam sleeves 7 are arranged offset from one another. With a simultaneous axial displacement of the individual cam sleeves 7, the individual axial slopes of the switching contour 2 arranged for each cam sleeve 7 lie on the inner circumference of the cam sleeves 7 in the same axial plane.

Die Schaltwelle 1 steht mit einem mit einem Aktuator 6 zur Erzeugung einer Relativverdrehung der Schaltwelle 1 gegenüber den Nockenhülsen 7 in Wirkverbindung. Der Aktuator 6 kann direkt oder wie in der Zeichnung dargestellt über ein Kurvengetriebe mit der Schaltwelle 1 verbunden sein. Das Kurvengetriebe besteht aus einer auf dem Umfang der Schaltwelle 1 angeordnete Schaltkontur 13 in der gleitend eine Schaltkugel 4 gelagert ist, die wiederum in einer am Innenumfang eines Verschiebestücks 5 angeordneten halbkugelförmigen Aufnahme gelagert ist. Das Verschiebestück 5 ist drehfest aber axial verschiebbar mit einer Nockenhülse 7 verbunden. Die Verbindung zwischen Nockenhülse 7 und Verschiebestück 5 erfolgt dabei über eine ineinandergreifende Axialverzahnung. Das Verschiebestück 5 ist mit einem Gehäuse der Brennkraftmaschine fest verbundenen Aktuator 6 in Wirkverbindung bringbar. Entsprechend der Ansteuerung des Aktuators 6 greift dabei ein an dem Aktuator 6 angeordneter Pin 11 in die am Umfang des Verschiebestücks 5 angeordnete Kontur 12 ein. Das Verschiebestück 5 ist entsprechend dem in der Zeichnung dargestelltem Doppelpfeil in beide Richtungen axial gegenüber einer Nockenhülse 7 verschiebbar.The switching shaft 1 is connected to one with an actuator 6 for generating a relative rotation of the switching shaft 1 relative to the cam sleeves 7 in operative connection. The actuator 6 may be connected directly or as shown in the drawing via a cam gear with the shift shaft 1. The cam mechanism consists of a arranged on the circumference of the switching shaft 1 switching contour 13 in the sliding a switching ball 4 is mounted, which in turn is mounted in a arranged on the inner circumference of a sliding piece 5 hemispherical receptacle. The sliding piece 5 is rotatably but axially displaceably connected to a cam sleeve 7. The connection between the cam sleeve 7 and sliding piece 5 takes place via an intermeshing axial toothing. The sliding piece 5 can be brought into operative connection with a housing of the internal combustion engine firmly connected actuator 6. In accordance with the activation of the actuator 6, a pin 11 arranged on the actuator 6 engages in the contour 12 arranged on the circumference of the displacement piece 5. The sliding piece 5 is axially displaceable relative to a cam sleeve 7 in both directions according to the double arrow shown in the drawing.

Die Funktion des variablen Ventiltriebs zur Realisierung einer Umschaltung zwischen den unterschiedlichen Nockenprofilen 9a, 9b und 9c ist folgende.The function of the variable valve train for realizing a changeover between the different cam profiles 9a, 9b and 9c is as follows.

Während des Eingriffes beispielsweise der mittleren Nockenprofile 9b der Nockenhülse 7 mit den Gaswechselventilen drehen sich die Nockenhülsen 7, die Schaltwelle 1 und das Verschiebestück 5 mit synchroner Drehzahl. Der Aktuator 6 steht nicht im Eingriff mit dem Verschiebestück 5. Eine Umschaltung zu einem andern Nockenprofil kann nur durchgeführt werden, wenn sich der Grundkreisabschnitt 10 im Eingriff mit dem Gaswechselventil bzw. dem Zwischenglied befindet. Zur Umschaltung des Eingriffes des Nockenprofils 9b auf das Gaswechselventil zu dem Nockenprofil 9a oder zu dem Nockenprofil 9c wird der Aktuator 6 durch eine entsprechende Ansteuerung aktiviert und mit dem Verschiebestück 5 in Eingriff gebracht. In dem beschrieben Ausführungsbeispiel erfolgt das dadurch, dass ein Pin 11 in Richtung des Verschiebestücks 5 ausgefahren wird und in die am Umfang des Verschiebestücks 5 angeordnete Kontur 12 einrastet. Entsprechend des angesteuerten Pins 11 wird das Verschiebestück 5 durch den in der Kontur 12 gleitenden Pin 11 nach rechts oder nach links, gemäß dem vorzunehmenden Schaltvorgang, gegenüber der Nockenhülse 7 axial verschoben. Über die in der Schaltkontur 13 gleitende Schaltkugel 4 wird die axiale Bewegung des Verschiebestücks 5 in eine Drehung der Schaltwelle 1 übersetzt. Dadurch entsteht eine Relativverdrehung der Schaltwelle 1 gegenüber den Nockenhülsen 7. Durch die Relativverdrehung gleitet der halbkugelförmig ausgebildete Teil des Schaltpins 3 in der Bahn der umlaufenden Schaltkontur 2 der Nockenhülse 7. Entsprechend der realisierten Relativverdrehung und der Ausführung der einzelnen mit jeder Nockenhülse 7 über die Schaltkugeln 3 in Wirkverbindung stehenden Schaltkonturen 2 erfolgt eine axiale Verschiebung der Nockenhülsen 7 gegeneinander und somit eine Umschaltung zwischen den einzelnen Nockenprofilen 9a, 9b und 9c.During the intervention, for example, the central cam profiles 9b of the cam sleeve 7 with the gas exchange valves, the cam sleeves 7, the switching shaft 1 and the sliding piece 5 rotate at a synchronous speed. The actuator 6 is not engaged with the sliding piece 5. A changeover to another cam profile can only be performed when the base circle portion 10 is in engagement with the gas exchange valve or the intermediate member. To switch the engagement of the cam profile 9b on the gas exchange valve to the cam profile 9a or to the cam profile 9c, the actuator 6 is activated by a corresponding control and brought into engagement with the sliding piece 5. In the described embodiment, this takes place in that a pin 11 is extended in the direction of the sliding piece 5 and engages in the contour 12 arranged on the circumference of the sliding piece 5. According to the driven pins 11, the sliding piece 5 is axially displaced relative to the cam sleeve 7 by the pin 11 sliding in the contour 12 to the right or to the left, according to the switching operation to be carried out. About the sliding in the switching contour 13 switching ball 4, the axial movement of the sliding piece 5 is translated into a rotation of the shift shaft 1. Due to the relative rotation of the hemispherical formed part of the switching pin 3 slides in the path of the rotating switching contour 2 of the cam sleeve 7. According to the realized relative rotation and the execution of the individual with each cam sleeve 7 via the switching balls 3 operatively connected switching contours 2 takes place an axial displacement of the cam sleeves 7 against each other and thus switching between the individual cam profiles 9a, 9b and 9c.

Die Verschiebung des Verschiebestücks 5 kann beispielsweise auch durch einen magnetisch auf das Verschiebestück 5 wirkenden Aktuator 6 erfolgen.The displacement of the sliding piece 5 can also be effected, for example, by an actuator 6 that acts magnetically on the sliding piece 5.

Der Vorteil der erfindungsgemäßen Lösung besteht in einem einfachen und klein bauenden Aufbau des Ventiltriebs, mit dem variabel für den Motor angepasste Ventilhubumschaltungen realisiert werden können. Aufstellung der verwendeten oBezugszeichen 1 Schaltwelle 2 Schaltkontur 3 Schaltpin 4 Schaltkugel 5 Verschiebestück 6 Aktuator 7 Nockenhülse 8 Verzahnung 9 Nockenprofil 9a kleines Nockenprofil 9b mittleres Nockenprofil 9c großes Nockenprofil 10 Grundkreisabschnitt 11 Pin 12 Kontur 13 Schaltkontur The advantage of the solution according to the invention consists in a simple and small construction of the valve train, can be realized with the variably adapted for the engine valve lift switching. <b> Listing of the used reference sign </ b> 1 shift shaft 2 switching contour 3 switch pin 4 switching ball 5 sliding piece 6 actuator 7 cam sleeve 8th gearing 9 cam profile 9a small cam profile 9b middle cam profile 9c big cam profile 10 Base circle portion 11 Pin code 12 contour 13 switching contour

Claims (6)

  1. A valve train for actuating gas exchange valves of an internal combustion engine, wherein a crankshaft of the internal combustion engine drives a camshaft, wherein the gas exchange valves can be engaged to different cam profiles by switching, characterized in that
    - a plurality of individual cam sleeves (7) are axially displaceable relative to one another and disposed so as to form the camshaft,
    - each of the plurality of individual cam sleeves (7) includes a plurality of different cam profiles (9a, 9b, 9c) each having a same base circle portion (10),
    - a switching shaft (1) is disposed inside the plurality of cam sleeves (7) and configured to rotate together with the plurality of cam sleeves (7),
    - a circumferential switching contour (2) is disposed inside each of the plurality of individual cam sleeves (7),
    - each cam sleeve (7) is operatively connected to a switching shaft (1) by a switching pin (3), which slides in the switching contour (2),
    - the switching shaft (1) is operatively connected to an actuator (6) to rotate the switching shaft (1) relative to the cam sleeves (7).
  2. A valve train according to claim 1, characterized in that the plurality of axially displaceable cam sleeves (7) are connected to each other by an axially extending toothing (8), in which the toothing (8) of the respective cam sleeves (7), being disposed adjacent to one another, are formed to be interconnected.
  3. A valve train according to claim 1 and 2, characterized in that the circumferential switching contour (2) includes multiple different axial inclinations.
  4. A valve train according to claim 1 to 3, characterized in that for a successive axial displacement of the respective cam sleeves (7) the respective axial inclinations of the switching contour (2) on the inner circumference of each cam sleeve (7) for each cam sleeve (7) are displaced relative to each other.
  5. A valve train according to claim 1 to 3, characterized in that for a simultaneous axial displacement of the respective cam sleeves (7) the respective axial inclinations of the switching contour (2) on the inner circumference of each cam sleeve (7) for each cam sleeve (7) are disposed in a similar axial plane.
  6. A valve train according to claim 1 to 5, characterized in that the switching shaft (1) is connected to a displacement piece (5), which is disposed so as to be rotationally engaged but axially displaceable on one of the plurality of cam sleeves (7), via a cam mechanism.
EP10760229.4A 2009-08-10 2010-08-03 Valve train for internal combustion engines for actuating gas exchange valves Not-in-force EP2464833B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009037269A DE102009037269B4 (en) 2009-08-10 2009-08-10 Valve train for internal combustion engines for actuating gas exchange valves
PCT/DE2010/000930 WO2011018073A2 (en) 2009-08-10 2010-08-03 Valve train for internal combustion engines for actuating gas exchange valves

Publications (2)

Publication Number Publication Date
EP2464833A2 EP2464833A2 (en) 2012-06-20
EP2464833B1 true EP2464833B1 (en) 2013-07-24

Family

ID=43531148

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10760229.4A Not-in-force EP2464833B1 (en) 2009-08-10 2010-08-03 Valve train for internal combustion engines for actuating gas exchange valves

Country Status (5)

Country Link
US (1) US8596238B2 (en)
EP (1) EP2464833B1 (en)
JP (1) JP5649237B2 (en)
DE (1) DE102009037269B4 (en)
WO (1) WO2011018073A2 (en)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009037270B4 (en) 2009-08-10 2011-04-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Valve train for internal combustion engines for actuating gas exchange valves
DE102009037268B3 (en) 2009-08-10 2011-04-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable valve drive for internal combustion engines for actuating gas exchange valves
DE102010014249A1 (en) 2010-04-08 2011-10-13 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Apparatus for displacement of relative rotational angle position between control shaft and cam sleeve, has annulus gear for planetary gear train that is placed on control shaft
DE102011108728B4 (en) 2011-07-27 2013-02-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Valve train for internal combustion engines for actuating gas exchange valves
DE102011054218B4 (en) 2011-10-06 2023-03-23 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Internal combustion engine and valve train for an internal combustion engine
DE102011116653B4 (en) * 2011-10-21 2023-11-09 Mercedes-Benz Group AG Valve drive device
DE102012008555B4 (en) * 2012-04-27 2014-11-27 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Device for a valve drive for switching the stroke of gas exchange valves of an internal combustion engine
US9605603B2 (en) * 2013-04-05 2017-03-28 Ford Global Technologies, Llc Position detection for lobe switching camshaft system
GB2519109A (en) * 2013-10-09 2015-04-15 Eaton Srl A valve train assembly
DE102014202439A1 (en) * 2014-02-11 2015-08-13 Mahle International Gmbh Internal combustion engine
DE112016004372T5 (en) 2015-11-06 2018-06-07 Borgwarner Inc. VALVE CONTROL SYSTEM THAT PROVIDES A VARIABLE VALVE HUB AND / OR VARIABLE VALVE TIME CONTROL
WO2018013464A1 (en) * 2016-07-14 2018-01-18 Borgwarner Inc. Shifting cam with internal actuator shaft
WO2020027826A1 (en) * 2018-08-01 2020-02-06 Borgwarner Inc. Timing system for operating an engine valve system and related method
US11441492B2 (en) * 2020-05-29 2022-09-13 GM Global Technology Operations LLC Deceleration cylinder cut-off with sliding cam

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3481314A (en) 1967-08-29 1969-12-02 Georges G Lecrenn Means for optimizing the performance of internal combustion engines
DE3934848A1 (en) 1989-10-19 1991-04-25 Ingelheim Peter Graf Von Camshaft with single control for several valve timings - has hollow shaft with peripheral slits firmly coupled to drive wheel
DE4230877A1 (en) 1991-09-30 1993-04-01 Volkswagen Ag Control for lift valve with two cams - comprises cam block containing two cams which is axially displaceable but non rotatable peripherally on camshaft
AT408127B (en) 1992-07-13 2001-09-25 Avl Verbrennungskraft Messtech Internal combustion engine with at least one camshaft that can be axially displaced by an adjusting device
DE4331977A1 (en) 1993-09-21 1995-03-23 Porsche Ag Variable valve timing
DE4416505A1 (en) * 1994-05-10 1995-11-16 Bayerische Motoren Werke Ag Cam shaft with turnable cams
DE19520117C2 (en) 1995-06-01 2002-04-11 Porsche Ag Valve train of an internal combustion engine
JPH10280930A (en) * 1997-04-09 1998-10-20 Toyota Motor Corp Valve system for internal combustion engine with multiple cylinder
DE19825307A1 (en) 1998-06-05 1999-12-09 Bayerische Motoren Werke Ag Valve control for an internal combustion engine
JP2002004823A (en) * 2000-06-23 2002-01-09 Honda Motor Co Ltd Valve system of internal combustion engine
DE10054623A1 (en) 2000-11-03 2002-05-08 Audi Ag Device for changeover of cam pack on camshaft to operate gas exchange valves has actuating element in form of pin movable radially outwards and in extended state interacting with slide tracks in guide section
JP4100054B2 (en) * 2002-06-20 2008-06-11 トヨタ自動車株式会社 Variable valve operating device for internal combustion engine
DE102004011586A1 (en) * 2003-03-21 2004-10-07 Audi Ag Valve gear for internal combustion engine has facility whereby in first and second axial positions of cam carrier first and second stop faces fixed on cam carrier bear against respective first and second stop faces fixed on cylinder head
EP1503048B1 (en) * 2003-07-19 2008-10-08 Dr. Ing. h.c. F. Porsche Aktiengesellschaft Valve drive for an internal combustion engine
DE102007016977A1 (en) * 2007-04-10 2008-10-16 Bayerische Motoren Werke Aktiengesellschaft Cam-operated valve stroke function adjusting device for use during operating and/or loading condition of internal combustion engine, has adjusting unit partially arranged within hollow shaft, and sleeve movable within shaft
DE102007027979B4 (en) 2007-06-19 2015-07-23 Audi Ag Valve train for gas exchange valves of an internal combustion engine with camshaft tunnel bearings
DE102007054978B4 (en) 2007-11-17 2023-12-14 Mercedes-Benz Group AG Valve drive device
DE102009017242B4 (en) 2009-04-09 2011-09-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Valve train for internal combustion engines for actuating gas exchange valves
DE102009037270B4 (en) 2009-08-10 2011-04-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Valve train for internal combustion engines for actuating gas exchange valves
DE102009037268B3 (en) 2009-08-10 2011-04-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable valve drive for internal combustion engines for actuating gas exchange valves

Also Published As

Publication number Publication date
EP2464833A2 (en) 2012-06-20
WO2011018073A2 (en) 2011-02-17
JP2013501872A (en) 2013-01-17
DE102009037269B4 (en) 2011-06-01
DE102009037269A1 (en) 2011-03-10
US8596238B2 (en) 2013-12-03
JP5649237B2 (en) 2015-01-07
WO2011018073A3 (en) 2011-04-28
US20120125273A1 (en) 2012-05-24

Similar Documents

Publication Publication Date Title
EP2464835B1 (en) Variable valve train for internal combustion engines for actuating gas exchange valves
EP2464833B1 (en) Valve train for internal combustion engines for actuating gas exchange valves
EP2464834B1 (en) Valve train for internal combustion engines for actuating gas exchange valves
DE102008061440B3 (en) Valve gear for actuating gas exchange valves of internal combustion engines
DE102010005790B4 (en) Valve gear for actuating gas exchange valves of internal combustion engines
DE102009017242B4 (en) Valve train for internal combustion engines for actuating gas exchange valves
AT408127B (en) Internal combustion engine with at least one camshaft that can be axially displaced by an adjusting device
EP2585687B1 (en) Adjustable camshaft
DE102007002802B4 (en) Method for switching a valve train of an internal combustion engine between a two-stroke and a four-stroke operation and valve train
DE102012008555B4 (en) Device for a valve drive for switching the stroke of gas exchange valves of an internal combustion engine
DE102010021903A1 (en) Valve train for operating gas shuttle valve of internal combustion engine, has shift piece connected with another shift piece propelled by shaft, where shifter rod and shift pieces are axially displaced in direction of actuators
EP3434871B1 (en) Sliding cam system
DE102011116653A1 (en) Valve drive device
DE102009057691A1 (en) Valve train for actuating gas exchange valves of internal combustion engine, has twistable adjusting shaft brought into engagement with and/or separable from cam shaft by adjusting gear for twisting adjusting shaft
DE102010025099A1 (en) Adjustable camshaft for use as part of valve train of engine, has adjusting element axially displaceable relative to longitudinal axis of shaft and mechanically coupled with cam packet over contact element
EP2196638B1 (en) Valve drive for actuating gas exchange valves of combustion engines
DE102009006894B4 (en) Device for switching operation of a hydraulic valve clearance compensation element
DE102014217584B4 (en) valve train device and shift gate
DE102012001303B4 (en) Verstellwellenbetätigung a valve train for internal combustion engines for the actuation of gas exchange valves
DE102004033798B4 (en) Valve gear for actuating gas exchange valves of internal combustion engines
EP3450708A1 (en) Sliding cam system
DE102017210661A1 (en) Valve train device for a multi-cylinder internal combustion engine
DE102017104631A1 (en) Device and method for valve lift control and internal combustion engine
DE102010021622A1 (en) Valve train for operating gas shuttle valve of multi-cylinder series internal combustion engine, has shifter rods arranged in cam shaft pipe and actively connected with switching contour of adjustable socket using synchronization pin
DE102014116479A1 (en) Arrangement of a switching camshaft and a drivable receptacle for this

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: 20120208

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

RIN1 Information on inventor provided before grant (corrected)

Inventor name: WERLER, ANDREAS

Inventor name: ARNOLD, THOMAS

Inventor name: WUTZLER, JOERG

Inventor name: NEUKIRCHNER, HEIKO

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

INTG Intention to grant announced

Effective date: 20130415

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM 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: AT

Ref legal event code: REF

Ref document number: 623601

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130815

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502010004159

Country of ref document: DE

Effective date: 20130919

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130724

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: HR

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: 20130724

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: 20130724

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: 20130828

Ref country code: IS

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: 20131124

Ref country code: NO

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: 20131024

Ref country code: LT

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: 20130724

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: 20131125

BERE Be: lapsed

Owner name: IAV G.M.B.H.

Effective date: 20130831

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

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: 20130724

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: 20130724

Ref country code: LV

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: 20130724

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: 20130724

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: 20130724

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: 20131025

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: 20130724

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

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: 20130724

Ref country code: MC

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: 20130724

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: 20130724

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: 20130724

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: 20130724

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: 20130724

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

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: 20130724

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: 20130724

Ref country code: BE

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

Effective date: 20130831

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

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140509

26N No opposition filed

Effective date: 20140425

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

Ref country code: IE

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

Effective date: 20130803

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010004159

Country of ref document: DE

Effective date: 20140425

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: 20130924

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: 20140803

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

Ref country code: CH

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

Effective date: 20140831

Ref country code: LI

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

Effective date: 20140831

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

Ref country code: SM

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: 20130724

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: 20130724

Ref country code: MT

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: 20130724

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: 20130803

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; INVALID AB INITIO

Effective date: 20100803

Ref country code: MK

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: 20130724

Ref country code: GB

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

Effective date: 20140803

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: 20130724

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 623601

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150803

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: 20150803

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

Ref country code: AL

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: 20130724

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

Ref country code: DE

Payment date: 20190911

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502010004159

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: 20210302