DE19611641C1 - Valve operating cam drive for combustion engines - Google Patents

Valve operating cam drive for combustion engines

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Publication number
DE19611641C1
DE19611641C1 DE19611641A DE19611641A DE19611641C1 DE 19611641 C1 DE19611641 C1 DE 19611641C1 DE 19611641 A DE19611641 A DE 19611641A DE 19611641 A DE19611641 A DE 19611641A DE 19611641 C1 DE19611641 C1 DE 19611641C1
Authority
DE
Germany
Prior art keywords
cam
camshaft
actuating
profile
valve train
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
DE19611641A
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German (de)
Inventor
Klaus Tiede
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.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche AG
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Filing date
Publication date
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Priority to DE19611641A priority Critical patent/DE19611641C1/en
Priority to EP97102494A priority patent/EP0798451B1/en
Priority to DE59700135T priority patent/DE59700135D1/en
Priority to KR1019970010097A priority patent/KR100416895B1/en
Priority to JP06933997A priority patent/JP3980699B2/en
Application granted granted Critical
Publication of DE19611641C1 publication Critical patent/DE19611641C1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—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
    • F01L1/344—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 changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—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 changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/053—Camshafts overhead type
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Abstract

The valves of the engine are operated by one of a number of cams (4a to 4c) which are integral with a sleeve (5) and which are located next to one another. The sleeve is connected to the camshaft (6) by e.g. splines so that it rotates with the shaft but can be moved axially. The sleeve is moved axially by rods (15,18), which can be fed-in radially towards the camshaft, and which engage with axial cam faces (9,10) on the endfaces of the sleeve. The sleeve is positioned on the camshaft by a spring-loaded ball (23) which engages with grooves in the sleeve bore.

Description

Die Erfindung betrifft einen Ventiltrieb einer Brennkraftmaschine nach der Gattung des Hauptanspruches.The invention relates to a valve train of an internal combustion engine according to the genus of Main claim.

Ein derartiger Ventiltrieb ist beispielsweise in der DE 42 30 877 A1 beschrieben und zeigt eine Nockenwelle, auf der ein Nockenblock mit zwei unterschiedlichen Nockenbahnen drehfest aber axial verschieblich geführt ist. Der Nockenblock wirkt mit einem Gaswechselventil der Brennkraftmaschine zusammen, wobei je nach Arbeitsstellung des Nockenblockes der Hubverlauf einer der beiden Nockenbahnen auf das Gaswechselventil übertragen wird. Im Bereich einer der beiden Stirnseiten des Nockenblockes ist in die Nockenwelle eine spiralförmige Führungsnut eingearbeitet, in die ein federnd gelagerter Schwenkbügel eingreifen kann. Dieser Schwenkbügel legt sich beim Eingreifen in die Spiralnut in Abhängigkeit von der Drehstellung der Nockenwelle an der Stirnseite des Nockenblockes an. Dadurch wird dieser gegen die Wirkung einer Druckfeder durch die Zwangsführung in der Führungsnut in axialer Richtung bewegt, so daß eine Umschaltung von einer ersten Nockenbahn, die mit dem Gaswechselventil zusammenwirkt, zur zweiten Nockenbahn erfolgt. Bei Erreichen der zweiten Arbeitsstellung des Nockenblockes wird dieser durch ein hydraulisch betätigtes Sperrelement festgesetzt. Die Spiralnut verläuft nur über einen Teil der Umfangsfläche, wobei am Ende der Spiralnut das Bügelelement außer Eingriff steht. Nach Lösen der hydraulischen Verriegelung kann der Nockenblock dann aufgrund der Wirkung der Druckfeder in seine Ausgangsstellung zurückbewegt werden. Die Spiralnut in der Nockenwelle ist dabei so ausgebildet und in einer definierten Winkelzuordnung zur Drehbewegung der Nockenwelle positioniert, daß das Verschieben des Nockenblockes nur während der Grundkreisphase der ersten Nockenbahn erfolgen kann. Die Nockenwelle für einen derartigen Ventiltrieb ist jedoch sehr aufwendig zu fertigen, da die Spiralnut für jeden zu betätigenden Nockenblock winkelrichtig zugeordnet werden muß. Darüber hinaus erfordert die Anbringung einer derartigen Nut in der Nockenwelle mehrere Bearbeitungsvorgänge, so daß insgesamt die Herstellung der Nockenwelle aufwendig und teuer ist. Weiterhin bedeutet die Anbringung einer derartigen Spiralnut in der Nockenwelle eine nicht unerhebliche Querschnittsverminderung, so daß unter Umständen der Wellendurchmesser relativ groß gewählt werden muß, um die aus dem Ventiltrieb resultierenden Kräfte und Momente aufnehmen zu können. Darüber hinaus ist die Betätigung mit einem federnd gelagerten Schwenkbügel aufwendig und erfordert einen nicht unerheblichen Einbauraum. Fehlschaltungen durch die federnde Lagerung sind nicht auszuschließen. Weiterhin ist durch eine derartige Betätigung nur die Umschaltung zwischen zwei Nockenbahnen möglich.Such a valve train is described for example in DE 42 30 877 A1 and shows a camshaft on which a cam block with two different Cam tracks are rotatably but axially displaceably guided. The cam block takes part a gas exchange valve of the internal combustion engine, depending on Working position of the cam block on the stroke of one of the two cam tracks the gas exchange valve is transmitted. In the area of one of the two end faces of the Cam block, a spiral guide groove is worked into the camshaft which a spring-loaded swivel bracket can engage. This swivel bracket attaches when engaging in the spiral groove depending on the rotational position of the Camshaft on the front of the cam block. This will make it against the Effect of a compression spring due to the positive guidance in the guide groove in the axial Direction moves, so that a switch from a first cam track that with the Gas exchange valve interacts, takes place to the second cam track. Upon reaching the second working position of the cam block is this by a hydraulic actuated locking element fixed. The spiral groove runs only over part of the Circumferential surface, the bracket element being disengaged at the end of the spiral groove. After releasing the hydraulic lock, the cam block can then due to the Effect of the compression spring can be moved back to its original position. The Spiral groove in the camshaft is designed and in a defined Angular assignment to the rotary movement of the camshaft positioned that the Shifting the cam block only during the base circle phase of the first Cam track can take place. However, the camshaft for such a valve train is very complex to manufacture because the spiral groove for each cam block to be operated must be assigned at the correct angle. In addition, the attachment of a such groove in the camshaft several machining operations, so that a total the production of the camshaft is complex and expensive. Furthermore, the means  Attaching such a spiral groove in the camshaft a not inconsiderable Cross-section reduction, so that under certain circumstances the shaft diameter relative must be chosen large to the forces and resulting from the valve train To be able to record moments. In addition, the actuation is springy stored swivel bracket complex and requires a not inconsiderable Installation space. Incorrect switching due to the resilient bearing cannot be ruled out. Furthermore, such an actuation only switches between two Cam tracks possible.

Demgegenüber ist es Aufgabe der Erfindung, einen derartigen Ventiltrieb einer Brennkraftmaschine so zu verbessern, daß die Nockenwelle zusammen mit den verschieblichen Nocken insgesamt kostengünstiger und einfacher hergestellt werden kann und die Zuordnung des Hubprofiles zur jeweiligen Drehlage des zu verschiebenden Nockens bei der Herstellung und Montage vereinfacht wird.In contrast, it is an object of the invention to provide such a valve train To improve the internal combustion engine so that the camshaft together with the Slidable cams can be manufactured overall cheaper and easier can and the assignment of the stroke profile to the respective rotational position of the moving cam in the manufacture and assembly is simplified.

Diese Aufgabe wird erfindungsgemäß mit den kennzeichnenden Merkmalen des Patentanspruches 1 gelöst. Durch Ausbildung des Hubprofiles am Nocken kann eine von der Welle unabhängige Bearbeitung des Hubprofiles erfolgen. Die Welle selbst wird dadurch in ihrem Querschnitt nicht mehr beeinträchtigt, so daß auch sehr geringe Wellendurchmesser möglich sind. Darüber hinaus ist die phasenrichtige Positionierung des Hubprofils zum jeweils axial verschieblichen Nocken einfacher zu gewährleisten, da die Nockenbahn und das Hubprofil am gleichen Bauteil ausgebildet sind. Lageabweichungen bzw. Phasenabweichungen von Nockengrundkreis und Hubprofil können dadurch bei der Montage nicht auftreten. Die Nockenwelle selbst kann dabei beispielsweise als gezogenes und daher preisgünstiges Bauteil gefertigt werden. Es ist weiterhin möglich, die Nockenwelle aus relativ preisgünstigem Material herzustellen, da sich die durch die Verschiebungsbewegung verursachten Kräfte und Momente im Nocken selber auswirken, der schon aufgrund seiner durch die Betriebsbelastungen notwendigen höheren Materialgüte gefertigt ist. Dabei wirkt der Nocken in vorteilhafter Weise mit einem radial zur Nockenwelle angeordneten Betätigungsstift zusammen, der verschieblich in Eingriff mit dem Hubprofil zu bringen ist. Eine derartige Anordnung kann mit sehr geringem Bau- und Platzaufwand im Zylinderkopf angeordnet werden und ermöglicht eine sichere Betätigung ohne die Gefahr von Fehlschaltungen.This object is achieved with the characterizing features of Claim 1 solved. By designing the lifting profile on the cam, one can machining of the stroke profile independent of the shaft. The wave itself is no longer affected in its cross section, so that even very small Shaft diameters are possible. In addition, the correct positioning of the lifting profile for the axially displaceable cam is easier to ensure because the cam track and the lifting profile are formed on the same component. Position deviations or phase deviations of the cam base circle and stroke profile cannot occur during assembly. The camshaft itself can do this for example as a drawn and therefore inexpensive component. It is still possible, the camshaft made of relatively inexpensive material to produce, since the forces and caused by the displacement movement Impact moments in the cam itself, which is already due to its Operating loads necessary higher material quality is made. The works Cams advantageously arranged radially to the camshaft Actuating pin together, which can be slidably brought into engagement with the lifting profile is. Such an arrangement can with very little construction and space  Cylinder head can be arranged and enables safe operation without the Danger of incorrect switching.

Ein besonders vorteilhafter Ventiltrieb mit drei verschiedenen Ventilhubkurven je Nocken ergibt sich, wenn drei Nockenbahnen hintereinander angeordnet werden. Das Verschieben des Nockens mit diesen drei Nockenbahnen erfolgt besonders vorteilhaft, wenn am Nocken zwei Hubprofilen ausgebildet sind, die an jeweils einer Stirnseite des Nockens ausgebildet sind.A particularly advantageous valve train with three different valve lift curves per cam results when three cam tracks are arranged one behind the other. The Moving the cam with these three cam tracks is particularly advantageous, if two cam profiles are formed on the cam, each on one end face of the Are formed.

Eine besonders vorteilhafte Betätigung des axial verschieblichen Nockens ergibt sich, wenn jedes Hubprofil mit zwei axial beabstandeten Betätigungsstiften zusammenwirkt, die beim Eingriff in das Hubprofil in Abhängigkeit von der Ausgangslage des Nockens Axialbewegungen auslösen. Insbesondere bei der Verwendung von zwei Hubprofilen kann damit auf die Verwendung von Rückstellelementen in Form von Druckfedern oder ähnlichem verzichtet werden. Dies führt auch dazu, daß die dadurch verursachten Fehlschaltungen vermieden werden können.A particularly advantageous actuation of the axially displaceable cam results if each lifting profile interacts with two axially spaced actuating pins that when engaging in the stroke profile depending on the starting position of the cam Trigger axial movements. Especially when using two lifting profiles can thus on the use of restoring elements in the form of compression springs or the like can be dispensed with. This also means that the caused Incorrect switching can be avoided.

Die Sicherung des Nockens in seiner jeweiligen Axialposition kann auf besonders einfache Weise durch federbelastete Rastelemente erfolgen, die in eine der jeweiligen Arbeitsstellung zugeordnete Rastnut am Nocken eingreifen.Securing the cam in its respective axial position can be particularly special done easily by spring-loaded latching elements, which in one of the respective Engage the locking groove assigned to the working position on the cam.

Weitere Vorteile und vorteilhafte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen und der Beschreibung.Further advantages and advantageous developments of the invention result from the Subclaims and the description.

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert. Letztere zeigt inAn embodiment of the invention is in the following description and Drawing explained in more detail. The latter shows in

Fig. 1 einen vereinfachten Querschnitt durch den Ventiltrieb der Brennkraftmaschine, Fig. 1 is a simplified cross-section through the valve drive of the internal combustion engine,

Fig. 2 einen Längsschnitt durch eine nur teilweise dargestellte Nockenwelle und Fig. 2 shows a longitudinal section through a camshaft and shown only partially

Fig. 3 eine Abwicklung des Nockenumfanges und der Hubprofile. Fig. 3 is a settlement of the cam circumference and the lifting profiles.

Der in Fig. 1 vereinfacht dargestellte Ventiltrieb der Brennkraftmaschine zeigt ein Gaswechselventil 1, das mit einem an sich bekannten Rollenschlepphebel 2 zusammenwirkt, dessen Rolle 3 an der Nockenbahn 4 eines Nockens 5 anliegt. Der Nocken 5 ist drehfest, aber axial verschieblich auf einer Nockenwelle 6 geführt, die auf an sich bekannte Weise angetrieben wird. Durch das Zusammenwirken der Nockenbahn 4 mit der Rolle 3 des Rollenschlepphebels 2 werden die Drehbewegungen der Nockenwelle 6 in Hubbewegungen des Gaswechselventils 1 überführt.The valve train of the internal combustion engine in simplified form in Fig. 1 shown is a gas exchange valve 1, which cooperates with a known roller cam 2, the roller 3 rests against the cam track 4 of a cam 5. The cam 5 is rotatably but axially displaceably guided on a camshaft 6 which is driven in a manner known per se. The interaction of the cam track 4 with the roller 3 of the roller finger follower 2 converts the rotary movements of the camshaft 6 into stroke movements of the gas exchange valve 1 .

Der Nocken 5 weist drei axial nebeneinander liegende Nockenbahnen 4a bis 4c (Fig. 2) auf, die sich in ihrem Ventilhubprofil, ihrer Hubhöhe und/oder ihrer Phasenlage unterscheiden. Die Breite der Nockenbahnen 4a bis 4c ist so gewählt, daß sie etwas größer als die Breite der Rolle 3 des Rollenschlepphebels 2 ist, so daß im Betrieb der Brennkraftmaschine jeweils eine Nockenbahn mit der Rolle 3 des Rollenschlepphebels 2 und damit mit dem Gaswechselventil 1 zusammenwirkt.The cam 5 has three axially adjacent cam tracks 4 a to 4 c ( FIG. 2), which differ in their valve lift profile, their lift height and / or their phase position. The width of the cam tracks 4 a to 4 c is chosen so that it is slightly larger than the width of the roller 3 of the roller finger follower 2 , so that in operation of the internal combustion engine, one cam track with the roller 3 of the roller finger follower 2 and thus with the gas exchange valve 1 cooperates.

Um den Rollenschlepphebel 2 in Eingriff mit einer der drei Nockenbahnen 4a bis 4c zu bringen, ist der Nocken 5 axial verschieblich auf der Nockenwelle 6 geführt. Diese weist dazu an ihrem Umfang eine axial verlaufende Profilierung auf, die mit einer entsprechenden Profilierung des Nockens 5 zusammenwirkt und so eine Übertragung der Drehbewegung bei gleichzeitiger Axialverschieblichkeit ermöglicht. Der Nocken 5 weist an seinen beiden Stirnseiten jeweils einen zylindrischen Fortsatz 7, 8 auf, in den jeweils eine sich über einen Teil des Umfanges erstreckendes Hubprofil 9, 10 in Form einer Vertiefung eingearbeitet ist. Im Bereich des zylindrischen Fortsatzes 7 sind zwei Betätigungselemente 11, 12 angeordnet, zwei weitere Betätigungselemente 13, 14 sind im Bereich des zylindrischen Fortsatzes 8 angeordnet. Diese Betätigungselemente 11 bis 14 haben jeweils einen Betätigungsstift 15 bis 18, der etwa radial zur Nockenwelle 6 verläuft und axial verschieblich ist. Im hier dargestellten Ausführungsbeispiel sind die Betätigungsstifte 15 bis 18 als hydraulische Kolben ausgebildet, die durch Druckbeaufschlagung der Betätigungselemente 11 bis 14 gegen die Wirkung einer Druckfeder 31 in Richtung auf die Nockenwelle 6 axial verschieblich sind. In order to bring the roller rocker arm 2 into engagement with one of the three cam tracks 4 a to 4 c, the cam 5 is guided axially displaceably on the camshaft 6 . For this purpose, it has an axially extending profiling on its circumference, which cooperates with a corresponding profiling of the cam 5 and thus enables the rotary movement to be transmitted with simultaneous axial displaceability. The cam 5 has on its two end faces each a cylindrical extension 7 , 8 , in each of which a lifting profile 9 , 10 extending over part of the circumference is incorporated in the form of a recess. Two actuating elements 11 , 12 are arranged in the region of the cylindrical extension 7 , two further actuating elements 13 , 14 are arranged in the region of the cylindrical extension 8 . These actuating elements 11 to 14 each have an actuating pin 15 to 18 , which extends approximately radially to the camshaft 6 and is axially displaceable. In the exemplary embodiment shown here, the actuating pins 15 to 18 are designed as hydraulic pistons which can be axially displaced in the direction of the camshaft 6 by pressurizing the actuating elements 11 to 14 against the action of a compression spring 31 .

Die Betätigungselemente 11 bis 14 mit ihren Betätigungsstiften 15 bis 18 sind so angeordnet, daß in Abhängigkeit von der axialen Stellung des Nockens 5 die Betätigungsstifte bei Druckbeaufschlagung der Betätigungselemente am zylindrischen Fortsatz 7 bzw. 8 anliegen und in Abhängigkeit von der Drehlage der Nockenwelle 6 und des Nockens 5 in das jeweils zugeordnete Hubprofil 9 oder 10 eingreifen. Greift einer der Betätigungsstife 15 bis 18 in das jeweils zugeordnete Hubprofil 9 oder 10 ein, wird der Nocken 5 aufgrund des Kurvenverlaufes des Hubprofils 9 oder 10 axial verschoben. Dabei wird durch das Zusammenwirken des Hubprofils 9 (linkes Hubprofil gem. Fig. 2) mit den Betätigungsstiften 15 oder 16 eine Verschiebung von der jeweiligen Ausgangslage nach links erzeugt. Durch Zusammenwirken eines der Betätigungsstifte 13 oder 14 mit dem Hubprofil 10 (rechtes Hubprofil gem. Fig. 2) wird aufgrund des Kurvenverlaufes entsprechend eine Verschiebung des Nockens 5 aus seiner jeweiligen Arbeitsstellung nach rechts verursacht. Durch Änderung der Steigungsrichtung des Hubprofils ist ohne weiteres eine Umkehrung der Verstellrichtung möglich.The actuating elements 11 to 14 with their actuating pins 15 to 18 are arranged such that, depending on the axial position of the cam 5, the actuating pins bear against the cylindrical extension 7 or 8 when the actuating elements are pressurized and depending on the rotational position of the camshaft 6 and Engage cam 5 in the respectively assigned lifting profile 9 or 10 . If one of the actuating pins 15 to 18 engages in the respectively assigned lifting profile 9 or 10 , the cam 5 is axially displaced due to the curve profile of the lifting profile 9 or 10 . The interaction of the lifting profile 9 (left lifting profile according to FIG. 2) with the actuating pins 15 or 16 produces a shift from the respective starting position to the left. By interaction of one of the actuating pins 13 or 14 with the stroke profile 10 (right stroke profile according to FIG. 2), the cam 5 correspondingly causes a shift of the cam 5 from its respective working position to the right. By changing the slope direction of the lifting profile, a reversal of the adjustment direction is easily possible.

Der Nocken 5 weist im Zusammenwirken mit den Betätigungselementen 11 bis 14 drei unterschiedliche Arbeitsstellungen I bis III auf, in denen jeweils eine der Nockenbahnen 4a bis 4c mit der Rolle 3 des Rollenschlepphebels 2 zusammenwirkt. Um den Nocken 5 in seiner jeweiligen Arbeitsstellung I bis III zu arretieren, weist er an seiner inneren Umfangsfläche drei ringförmig umlaufende Nuten 19 bis 21 auf. In der Nockenwelle 6 ist in einer zylindrischen Vertiefung 22 eine Rastkugel 23 geführt, die durch Wirkung eines Federelementes 24 in eine der drei Nuten 19 bis 21 eingreift.In cooperation with the actuating elements 11 to 14, the cam 5 has three different working positions I to III, in each of which one of the cam tracks 4 a to 4 c cooperates with the roller 3 of the roller finger follower 2 . In order to lock the cam 5 in its respective working position I to III, it has three annular circumferential grooves 19 to 21 on its inner peripheral surface. In the camshaft 6 , a detent ball 23 is guided in a cylindrical recess 22, which engages in one of the three grooves 19 to 21 by the action of a spring element 24 .

In der in Fig. 2 dargestellten Lage des Nockens ist dieser durch die Rastkugel 23 im Zusammenwirken mit der Nut 20 in der mittleren Arbeitsstellung II rastiert. In dieser Arbeitsstellung II wirkt die Rolle 3 des Rollenschlepphebels 2 mit der Nockenbahn 4b zusammen. Soll aus dieser Ausgangslage der Ventiltrieb so umgeschaltet werden, daß das Gaswechselventil dem Hubverlauf der Nockenbahn 4c folgt, wird der Betätigungsstift 15 durch Druckbeaufschlagung des Betätigungselementes 11 abgesenkt. Dieser liegt dann auf dem zylindrischen Fortsatz 7 an und greift bei Erreichen der zugeordneten Drehlage des Nockens in das Hubprofil 9 ein, in dessen weiterem Verlauf der Nocken nach links bewegt wird. Fig. 3 zeigt dabei im wesentlichen eine Darstellung der Wirkebenen, d. h. die Zuordnung von Hubprofilen und Nockenverlauf (Grundkreisbereich 25, 25′ und Erhebungsbereich 30, 30′). Die winkelrichtige Zuordnung der Hubprofile zum Nockenverlauf ist abhängig von der Winkelposition der Verstellelemente. Am Ende des Hubprofils 9 hat der Nocken 5 seine linke Endstellung erreicht, die der Arbeitsstellung III entspricht, und in der die Rolle 3 mit der Nockenbahn 4c zusammenwirkt. Die Hubprofile 9 und 10 sind dabei in ihrer Erstreckung und Winkelzuordnung so ausgebildet, daß die axiale Verschiebung nur erfolgt, solange die Rolle 3 im Grundkreisbereich 25 an der jeweiligen Nockenbahnen 4a bis 4c anliegt. Die Nockenbahnen 4a bis 4c sind dabei so ausgebildet, daß sie jeweils einen Grundkreisbereich 25 aufweisen, der zumindest über den wesentlichen Teil seiner Länge parallel und in gleicher Höhe zu den Grundkreisbereichen der benachbarten Nockenbahnen verläuft. Diesem Grundkreisbereich 25 der Nockenbahnen ist der Grundkreisbereich 25′ der Hubprofile 9, 10 bzw. der zylindrischen Fortsätze 7, 8 zugeordnet, der in Abhängigkeit von der räumlichen Lage der Verstellelemente winkelverschoben ist. Nach Erreichen der Schaltstellung III wird das Betätigungselement 11 drucklos geschaltet, so daß der Betätigungsstift 11 durch die Wirkung der Druckfeder 31 in seine Ausgangslage zurückbewegt wird. Der Nocken 5 wird aufgrund der Rastierung in seiner Schaltstellung gehalten. Wird die Druckbeaufschlagung des jeweiligen Verstellelementes nach Erreichen der Endstellung des Nockens nicht zurückgenommen, bleibt dies ohne Einfluß auf die Verstellbewegung. Der jeweilige Betätigungsstift liegt dann weiterhin am jeweiligen zylindrischen Fortsatz an, gelangt aber erst im Auslaufbereich des jeweiligen Hubprofils mit diesem in Eingriff, so daß keine Verstellung erfolgt. Der jeweilige Einlaufbereich 26, 27 und Auslaufbereich 28, 29 der Hubprofile 9, 10 gehen ohne Stufe in die Umfangsfläche der zylindrischen Fortsätze über.In the position of the cam shown in FIG. 2, it is locked in the middle working position II by the detent ball 23 in cooperation with the groove 20 . In this working position II, the roller 3 of the roller finger follower 2 interacts with the cam track 4 b. If the valve train is to be switched over from this starting position such that the gas exchange valve follows the stroke of the cam track 4 c, the actuating pin 15 is lowered by pressurizing the actuating element 11 . This then lies on the cylindrical extension 7 and, when the assigned rotational position of the cam is reached, engages in the lifting profile 9 , in the course of which the cam is moved to the left. Fig. 3 shows essentially a representation of the active levels, ie the assignment of stroke profiles and cam profile (base circle area 25 , 25 'and elevation area 30 , 30 '). The correct assignment of the stroke profiles to the cam profile depends on the angular position of the adjustment elements. At the end of the lifting profile 9 , the cam 5 has reached its left end position, which corresponds to the working position III, and in which the roller 3 interacts with the cam track 4 c. The stroke profiles 9 and 10 are designed in their extension and angular assignment so that the axial displacement takes place only as long as the roller 3 in the base circle region 25 abuts the respective cam tracks 4 a to 4 c. The cam tracks 4 a to 4 c are designed such that they each have a base circle region 25 which runs at least over the major part of its length parallel and at the same height to the base circle regions of the adjacent cam tracks. This base circle region 25 of the cam tracks is assigned the base circle region 25 'of the lifting profiles 9 , 10 or the cylindrical extensions 7 , 8 , which is angularly displaced depending on the spatial position of the adjusting elements. After switching position III is reached, the actuating element 11 is depressurized, so that the actuating pin 11 is moved back into its starting position by the action of the compression spring 31 . The cam 5 is held in its switching position due to the detent. If the pressure applied to the respective adjusting element is not removed after the cam has reached the end position, this has no influence on the adjusting movement. The respective actuating pin then remains in contact with the respective cylindrical extension, but only comes into engagement with it in the outlet area of the respective lifting profile, so that no adjustment takes place. The respective inlet area 26 , 27 and outlet area 28 , 29 of the lifting profiles 9 , 10 merge into the circumferential surface of the cylindrical extensions without a step.

Soll der Nocken aus der Arbeitsstellung III in die mittlere Arbeitsstellung II zurückbewegt werden, wird das Betätigungselement 13 druckbeaufschlagt, so daß der Betätigungsstift 17 am zylindrischen Fortsatz 8 anliegt und bei Erreichen der Grundkreisphase in das Hubprofil 10 eingreift. Durch das Zusammenwirken des Betätigungsstifes 17 und des Hubprofils 10 wird der Nocken in die mittlere Arbeitsstellung II zurückbewegt.If the cam is to be moved back from the working position III into the middle working position II, the actuating element 13 is pressurized so that the actuating pin 17 rests on the cylindrical extension 8 and engages in the stroke profile 10 when the base circle phase is reached. Through the interaction of the actuating pin 17 and the lifting profile 10 , the cam is moved back into the middle working position II.

Eine Verschiebung des Nockens aus der mittleren Arbeitsstellung II in die rechte Arbeitsstellung I erfolgt durch Beaufschlagung des Betätigungselementes 14, das ebenfalls mit dem Hubprofil 10 zusammenwirkt und den Nocken nach rechts bewegt. Das Zurückstellen des Nockens in die mittlere Arbeitsstellung II erfolgt auf analoge Weise durch Druckbeaufschlagen des Betätigungselementes 12, das mit dem Hubprofil 9 zusammenwirkt.The cam is shifted from the middle working position II into the right working position I by actuating the actuating element 14 , which also interacts with the lifting profile 10 and moves the cam to the right. The cam is returned to the middle working position II in an analogous manner by pressurizing the actuating element 12 which interacts with the lifting profile 9 .

Durch geeignete Aussteuerung der Betätigungselemente 11 bis 14 wird dabei sichergestellt, daß jeweils nur ein Betätigungsstift 15 bis 18 abgesenkt werden kann, während die drei anderen Betätigungsstifte in ihrer Ausgangslage zurückbewegt sind und dort verbleiben.Suitable control of the actuating elements 11 to 14 ensures that only one actuating pin 15 to 18 can be lowered at a time, while the three other actuating pins are moved back into their initial position and remain there.

Im Gegensatz zum hier dargestellten Ausführungsbeispiel kann die Betätigung der Betätigungselemente 11 bis 14 beispielsweise auch pneumatisch, rein mechanisch oder elektromagnetisch erfolgen. Es ist auch möglich anstelle des dargestellten und beschriebenen Rollenschlepphebels andere - an sich bekannte - Übertragungsmechanismen einzusetzen, die die Drehbewegung des Nockens in eine Hubbewegung des Gaswechselventils überführen.In contrast to the exemplary embodiment shown here, the actuation elements 11 to 14 can also be actuated pneumatically, purely mechanically or electromagnetically. Instead of the roller finger follower shown and described, it is also possible to use other - known per se - transmission mechanisms which convert the rotary movement of the cam into a lifting movement of the gas exchange valve.

Claims (6)

1. Ventiltrieb einer Brennkraftmaschine mit einer Nockenwelle (6) mit Nocken (5) zur Betätigung von Gaswechselventilen (1), von denen mindestens ein Nocken mit mehreren axial hintereinander angeordneten Nockenbahnen (4a bis 4c) versehen und drehfest aber axialverschieblich auf der Nockenwelle geführt ist, und mit einem in Richtung der Nockenwellenachse wir­ kenden Hubprofil (9, 10), das mit mindestens einem Betätigungselement (11 bis 14) zum axialen Verschieben des Nockens zusammenwirkt, dadurch gekennzeichnet, daß das Hubprofil (9, 10) am Nocken (5) ausgebildet ist, und das Betätigungselement (11 bis 14) einen radial zur Nockenwelle angeordneten Betätigungsstift (15 bis 18) aufweist, der radial verschieblich in oder außer Eingriff mit dem Hubprofil (9, 10) zu bringen ist.1.Valve drive of an internal combustion engine with a camshaft ( 6 ) with cams ( 5 ) for actuating gas exchange valves ( 1 ), of which at least one cam is provided with a plurality of cam tracks ( 4 a to 4 c) arranged axially one behind the other and is rotationally fixed but axially displaceable on the camshaft is guided, and with a stroke profile ( 9 , 10 ) in the direction of the camshaft axis, which cooperates with at least one actuating element ( 11 to 14 ) for axially displacing the cam, characterized in that the stroke profile ( 9 , 10 ) on the cam ( 5 ), and the actuating element ( 11 to 14 ) has an actuating pin ( 15 to 18 ) arranged radially to the camshaft, which can be brought radially displaceably into or out of engagement with the lifting profile ( 9 , 10 ). 2. Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß das Hubprofil (9, 10) durch eine Kurvenbahn gebildet wird, die in einem benachbart zu den Nockenbahnen angeordneten Zylinderabschnitt (7, 8) ausgebildet ist.2. Valve train according to claim 1, characterized in that the lifting profile ( 9, 10 ) is formed by a cam track which is formed in a cylinder section ( 7 , 8 ) arranged adjacent to the cam tracks. 3. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß der verschiebliche Nocken (5) mit drei hintereinander angeordneten Nockenbahnen (4a bis 4c) versehen ist, und daß am Nocken zwei Hubprofile (9, 10) ausgebildet sind, zwischen denen die Nockenbahnen verlaufen.3. Valve train according to one of the preceding claims, characterized in that the displaceable cam ( 5 ) with three successively arranged cam tracks ( 4 a to 4 c) is provided, and in that two cam profiles ( 9 , 10 ) are formed on the cam, between which the cam tracks run. 4. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß jedes Hubprofil (9, 10) in Abhängigkeit von der axialen Schaltstellung des Nockens (5) mit einem von jeweils zwei in axialer Richtung der Nockenwelle beabstandet angeordneten Betätigungsstiften (15, 16; 17, 18) zusammenwirkt.4. Valve gear according to one of the preceding claims, characterized in that each lifting profile ( 9 , 10 ) depending on the axial switching position of the cam ( 5 ) with one of two actuating pins ( 15 , 16 ; 17) spaced apart in the axial direction of the camshaft , 18 ) cooperates. 5. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß zwischen dem verschieblichen Nocken (5) und der Nockenwelle (6) ein Rastmittel (19 bis 24) angeordnet ist, das den Nocken in seiner jeweiligen axialen Schaltstellung verrastet. 5. Valve train according to one of the preceding claims, characterized in that between the displaceable cam ( 5 ) and the camshaft ( 6 ) a locking means ( 19 to 24 ) is arranged, which latches the cam in its respective axial switching position. 6. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß das Rastmittel eine federbelastete Kugel (23) ist, die in jeweils eine Rastnut (19, 20, 21) eingreift.6. Valve train according to one of the preceding claims, characterized in that the latching means is a spring-loaded ball ( 23 ) which engages in a respective latching groove ( 19 , 20 , 21 ).
DE19611641A 1996-03-25 1996-03-25 Valve operating cam drive for combustion engines Expired - Fee Related DE19611641C1 (en)

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DE19611641A DE19611641C1 (en) 1996-03-25 1996-03-25 Valve operating cam drive for combustion engines
EP97102494A EP0798451B1 (en) 1996-03-25 1997-02-15 Valve control of an internal combustion engine
DE59700135T DE59700135D1 (en) 1996-03-25 1997-02-15 Valve train of an internal combustion engine
KR1019970010097A KR100416895B1 (en) 1996-03-25 1997-03-24 Valve drive device of internal combustion engine
JP06933997A JP3980699B2 (en) 1996-03-25 1997-03-24 Valve driving device for internal combustion engine

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KR970065972A (en) 1997-10-13
EP0798451B1 (en) 1999-04-21

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