EP0798451A1 - Valve control of an internal combustion engine - Google Patents

Valve control of an internal combustion engine Download PDF

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Publication number
EP0798451A1
EP0798451A1 EP97102494A EP97102494A EP0798451A1 EP 0798451 A1 EP0798451 A1 EP 0798451A1 EP 97102494 A EP97102494 A EP 97102494A EP 97102494 A EP97102494 A EP 97102494A EP 0798451 A1 EP0798451 A1 EP 0798451A1
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EP
European Patent Office
Prior art keywords
cam
camshaft
actuating
lifting
tracks
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Granted
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EP97102494A
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German (de)
French (fr)
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EP0798451B1 (en
Inventor
Klaus Tiede
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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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

Definitions

  • the invention relates to a valve train of an internal combustion engine according to the preamble of the main claim.
  • 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 is rotatably but axially displaceably guided.
  • the cam block interacts with a gas exchange valve of the internal combustion engine, the stroke course of one of the two cam tracks being transmitted to the gas exchange valve depending on the working position of the cam block.
  • a spiral guide groove is worked into the camshaft, into which a spring-mounted swivel bracket can engage. This swivel bracket engages in the spiral groove depending on the rotational position of the camshaft on the end face of the cam block.
  • the spiral groove in the camshaft is designed and positioned in a defined angular assignment to the rotary movement of the camshaft in such a way that the cam block can only be moved during the base circle phase of the first cam track.
  • the camshaft for such a valve train is very complex to manufacture, since the spiral groove must be assigned the correct angle for each cam block to be actuated.
  • the creation of such a groove in the camshaft requires several machining operations, so that the overall production of the camshaft is complex and expensive.
  • the means Attaching such a spiral groove in the camshaft has a not inconsiderable reduction in cross-section, so that under certain circumstances the shaft diameter must be chosen to be relatively large in order to be able to absorb the forces and moments resulting from the valve train.
  • the operation with a spring-loaded swivel bracket is complex and requires a not inconsiderable installation space. Incorrect switching due to the resilient bearing cannot be ruled out. Furthermore, such an actuation only enables switching between two cam tracks.
  • the lifting profile can be processed independently of the shaft.
  • the cross section of the shaft itself is no longer affected, so that very small shaft diameters are also possible.
  • the camshaft itself can be manufactured, for example, as a drawn and therefore inexpensive component.
  • camshaft from relatively inexpensive material, since the forces and moments caused by the displacement movement have an effect in the cam itself, which is already manufactured due to the higher material quality required by the operating loads.
  • the cam advantageously interacts with an actuating pin arranged radially to the camshaft, which can be slidably brought into engagement with the lifting profile.
  • Such an arrangement can with very little construction and space Cylinder head can be arranged and enables safe operation without the risk of incorrect switching.
  • a particularly advantageous valve train with three different lift profiles per cam results if three cam tracks are arranged one behind the other. The displacement of the cam with these three cam tracks takes place particularly advantageously if two lift curves are formed on the cam, each of which is formed on one end face of the cam.
  • a particularly advantageous actuation of the axially displaceable cam results if each stroke curve interacts with two spaced actuation pins which trigger axial movements when the cam curve is engaged, depending on the starting position of the cam.
  • the use of return elements in the form of compression springs or the like can be dispensed with. This also leads to the fact that the switching errors caused thereby can be avoided.
  • the cam can be secured in its respective axial position in a particularly simple manner by spring-loaded latching elements which engage in a latching groove on the cam assigned to the respective working position.
  • the valve train of the internal combustion engine shown in simplified form in FIG. 1 shows a gas exchange valve 1, which is equipped with a roller rocker arm 2 known per se cooperates, the roller 3 abuts 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.
  • the cam 5 has three axially adjacent cam tracks 4a to 4c (FIG. 2), which differ in their stroke profile, their stroke height and / or their phase position.
  • the width of the cam tracks 4a to 4c is selected so that it is somewhat larger than the width of the roller 3 of the roller finger follower 2, so that one cam track interacts with the roller 3 of the roller finger follower 2 and thus with the gas exchange valve 1 during operation of the internal combustion engine.
  • the cam 5 In order to bring the roller rocker arm 2 into engagement with one of the three cam tracks 4a to 4c, the cam 5 is guided on the camshaft 6 in an axially displaceable manner.
  • 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 a cylindrical extension 7, 8, in each of which a stroke curve 9, 10 extending over part of the circumference is incorporated in the form of a depression.
  • 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.
  • 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.
  • 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.
  • 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 apply when the actuating elements are pressurized on the cylindrical extension 7 or 8 and depending on the rotational position of the camshaft 6 and Engage cam 5 in the respectively assigned stroke curve 9 or 10. If one of the actuating pins 15 to 18 engages in the respectively assigned stroke curve 9 or 10, the cam 5 is axially displaced due to the curve profile of the stroke curve 9 or 10. The interaction of the stroke curve 9 (left stroke curve according to FIG. 2) with the actuating pins 15 or 16 produces a shift from the respective starting position to the left.
  • the cam 5 By interaction of one of the actuating pins 13 or 14 with the stroke curve 10 (right stroke curve 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 stroke curve, a reversal of the adjustment direction is easily possible.
  • the cam 5 In cooperation with the actuating elements 11 to 14, the cam 5 has three different working positions to in which one of the cam tracks 4a to 4c cooperates with the roller 3 of the roller finger follower 2. To the cam 5 in its respective working position to to lock, it has on its inner peripheral surface three annular circumferential grooves 19 to 21. 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.
  • the correct angular assignment of the lifting curves to the cam profile depends on the angular position of the adjusting elements.
  • the cam 5 has reached its left end position, that of the working position corresponds, and in which the roller 3 cooperates with the cam track 4c.
  • the stroke curves 9 and 10 are designed in their extension and angular assignment so that the axial displacement only takes place as long as the roller 3 in the base circle region 25 abuts the respective cam tracks 4a to 4c.
  • the cam tracks 4a to 4c are designed in such a way 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 curves 9, 10 or the cylindrical extensions 7, 8, which is angularly shifted depending on the spatial position of the adjusting elements.
  • the actuating element 11 is depressurized so that the actuating pin 11 is moved back into its initial 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 is then still in contact with the respective cylindrical extension, but only comes into engagement with it in the outlet area of the respective stroke curve, so that no adjustment takes place.
  • the respective inlet area 26, 27 and outlet area 28, 29 of the lifting curves 9, 10 merge into the circumferential surface of the cylindrical extensions without a step.
  • the actuating element 13 is pressurized so that the actuating pin 17 rests on the cylindrical extension 8 and when the Base circle phase engages in the cam 10. By the interaction of the actuating pin 17 and the cam 10, the cam is in the middle working position moved back.
  • a shift of the cam from the middle working position in the right working position takes place by acting on the actuating element 14, which also interacts with the cam 10 and moves the cam to the right.
  • the return of the cam to the middle working position takes place in an analogous manner by pressurizing the actuating element 12, which interacts with the stroke curve 9.
  • 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.
  • the actuation elements 11 to 14 can also be actuated pneumatically, purely mechanically or electromagnetically.
  • 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.

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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 preamble of the 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 is rotatably but axially displaceably guided. The cam block interacts with a gas exchange valve of the internal combustion engine, the stroke course of one of the two cam tracks being transmitted to the gas exchange valve depending on the working position of the cam block. In the area of one of the two end faces of the cam block, a spiral guide groove is worked into the camshaft, into which a spring-mounted swivel bracket can engage. This swivel bracket engages in the spiral groove depending on the rotational position of the camshaft on the end face of the cam block. As a result, this is moved in the axial direction against the action of a compression spring by the positive guidance in the guide groove, so that a switchover from a first cam track, which cooperates with the gas exchange valve, to the second cam track takes place. When the second working position of the cam block is reached, it is fixed by a hydraulically operated locking element. The spiral groove extends 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 be moved back into its starting position due to the action of the compression spring. The spiral groove in the camshaft is designed and positioned in a defined angular assignment to the rotary movement of the camshaft in such a way that the cam block can only be moved during the base circle phase of the first cam track. However, the camshaft for such a valve train is very complex to manufacture, since the spiral groove must be assigned the correct angle for each cam block to be actuated. In addition, the creation of such a groove in the camshaft requires several machining operations, so that the overall production of the camshaft is complex and expensive. Furthermore, the means Attaching such a spiral groove in the camshaft has a not inconsiderable reduction in cross-section, so that under certain circumstances the shaft diameter must be chosen to be relatively large in order to be able to absorb the forces and moments resulting from the valve train. In addition, the operation with a spring-loaded swivel bracket is complex and requires a not inconsiderable installation space. Incorrect switching due to the resilient bearing cannot be ruled out. Furthermore, such an actuation only enables switching between two cam tracks.

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 improve such a valve train of an internal combustion engine so that the camshaft together with the displaceable cams can be manufactured overall more cost-effectively and easily and the assignment of the stroke profile to the respective rotational position of the cam to be displaced is simplified during manufacture and assembly .

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.
Ein besonders vorteilhafter Ventiltrieb mit drei verschiedenen Hubprofilen 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 Hubkurven ausgebildet sind, die an jeweils einer Stirnseite des Nockens ausgebildet sind.This object is achieved with the characterizing features of claim 1. By forming the lifting profile on the cam, the lifting profile can be processed independently of the shaft. The cross section of the shaft itself is no longer affected, so that very small shaft diameters are also possible. In addition, it is easier to ensure that the stroke profile is positioned in phase with the axially displaceable cam, since the cam track and the stroke profile are formed on the same component.
This means that positional deviations or phase deviations of the cam base circle and the lifting profile cannot occur during assembly. The camshaft itself can be manufactured, for example, as a drawn and therefore inexpensive component. It is also possible to manufacture the camshaft from relatively inexpensive material, since the forces and moments caused by the displacement movement have an effect in the cam itself, which is already manufactured due to the higher material quality required by the operating loads. The cam advantageously interacts with an actuating pin arranged radially to the camshaft, which can be slidably brought into engagement with the lifting profile. Such an arrangement can with very little construction and space Cylinder head can be arranged and enables safe operation without the risk of incorrect switching.
A particularly advantageous valve train with three different lift profiles per cam results if three cam tracks are arranged one behind the other. The displacement of the cam with these three cam tracks takes place particularly advantageously if two lift curves are formed on the cam, each of which is formed on one end face of the cam.

Eine besonders vorteilhafte Betätigung des axial verschieblichen Nockens ergibt sich, wenn jede Hubkurve mit zwei beabstandeten Betätigungsstiften zusammenwirkt, die beim Eingriff in die Hubkurve in Abhängigkeit von der Ausgangslage des Nockens Axialbewegungen auslösen. Insbesondere bei der Verwendung von zwei Hubkurven 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 stroke curve interacts with two spaced actuation pins which trigger axial movements when the cam curve is engaged, depending on the starting position of the cam. In particular when using two stroke curves, the use of return elements in the form of compression springs or the like can be dispensed with. This also leads to the fact that the switching errors caused thereby 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.The cam can be secured in its respective axial position in a particularly simple manner by spring-loaded latching elements which engage in a latching groove on the cam assigned to the respective working position.

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 in

Fig.1
einen vereinfachten Querschnitt durch den Ventiltrieb der Brennkraftmaschine,
Fig. 2
einen Längsschnitt durch eine nur teilweise dargestellte Nockenwelle und
Fig. 3
eine Abwicklung des Nockenumfanges und der Hubkurven.
An embodiment of the invention is explained in more detail in the following description and drawing. The latter shows in
Fig. 1
a simplified cross section through the valve train of the internal combustion engine,
Fig. 2
a longitudinal section through a camshaft only partially shown and
Fig. 3
a handling of the cam circumference and the lifting curves.

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 shown in simplified form in FIG. 1 shows a gas exchange valve 1, which is equipped with a roller rocker arm 2 known per se cooperates, the roller 3 abuts 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 Hubprofil, 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 4a to 4c (FIG. 2), which differ in their stroke profile, their stroke height and / or their phase position. The width of the cam tracks 4a to 4c is selected so that it is somewhat larger than the width of the roller 3 of the roller finger follower 2, so that one cam track interacts with the roller 3 of the roller finger follower 2 and thus with the gas exchange valve 1 during operation of the internal combustion engine.

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 erstreckende Hubkurve 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 4a to 4c, the cam 5 is guided on the camshaft 6 in an axially displaceable manner. 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 a cylindrical extension 7, 8, in each of which a stroke curve 9, 10 extending over part of the circumference is incorporated in the form of a depression. 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 anlegen und in Abhängigkeit von der Drehlage der Nockenwelle 6 und des Nockens 5 in die jeweils zugeordnete Hubkurve 9 oder 10 eingreifen. Greift einer der Betätigungsstifte 15 bis 18 in die jeweils zugeordnete Hubkurve 9 oder 10 ein, wird der Nocken 5 aufgrund des Kurvenverlaufes der Hubkurve 9 oder 10 axial verschoben. Dabei wird durch das Zusammenwirken der Hubkurve 9 (linke Hubkurve 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 der Hubkurve 10 (rechte Hubkurve gem. Fig 2) wird aufgrund des Kurvenverlaufes entsprechend eine Verschiebung des Nockens 5 aus seiner jeweiligen Arbeitsstellung nach rechts verursacht. Durch Änderung der Steigungsrichtung der Hubkurve 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 apply when the actuating elements are pressurized on the cylindrical extension 7 or 8 and depending on the rotational position of the camshaft 6 and Engage cam 5 in the respectively assigned stroke curve 9 or 10. If one of the actuating pins 15 to 18 engages in the respectively assigned stroke curve 9 or 10, the cam 5 is axially displaced due to the curve profile of the stroke curve 9 or 10. The interaction of the stroke curve 9 (left stroke curve 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 curve 10 (right stroke curve 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 stroke curve, a reversal of the adjustment direction is easily possible.

Der Nocken 5 weist im Zusammenwirken mit den Betätigungselementen 11 bis 14 drei unterschiedliche Arbeitsstellungen

Figure imgb0001
bis
Figure imgb0002
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
Figure imgb0001
bis
Figure imgb0002
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
Figure imgb0001
to
Figure imgb0002
in which one of the cam tracks 4a to 4c cooperates with the roller 3 of the roller finger follower 2.
To the cam 5 in its respective working position
Figure imgb0001
to
Figure imgb0002
to lock, it has on its inner peripheral surface three annular circumferential grooves 19 to 21. 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

Figure imgb0005
rastiert. In dieser Arbeitsstellung
Figure imgb0005
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 die Hubkurve 9 ein, in deren weiterem Verlauf der Nocken nach links bewegt wird. Fig. 3 zeigt dabei im wesentlichen eine Darstellung der Wirkebenen, d. h. die Zuordnung von Hubkurbven und Nockenverlauf (Grundkreisbereich 25, 25' und Erhebungsbereich 30, 30'). Die winkelrichtige Zuordnung der Hubkurven zum Nockenverlauf ist abhängig von der Winkelposition der Verstellelemente. Am Ende der Hubkurve 9 hat der Nocken 5 seine linke Endstellung erreicht, die der Arbeitsstellung
Figure imgb0002
entspricht, und in der die Rolle 3 mit der Nockenbahn 4c zusammenwirkt. Die Hubkurven 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 Hubkurven 9, 10 bzw. der zylindrischen Fortsätze 7, 8 zugordnet, der in Abhängikeit von der räumlichen Lage der Verstellelemente winkelverschoben ist. Nach Erreichen der Schaltstellung
Figure imgb0002
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 der jeweiligen Hubkurve mit dieser in Eingriff, so daß keine Verstellung erfolgt. Der jeweilige Einlaufbereich 26, 27 und Auslaufbereich 28, 29 der Hubkurven 9, 10 gehen ohne Stufe in die Umfangsfläche der zylindrischen Fortsätze über.In the position of the cam shown in FIG. 2, this is in the middle working position by the locking ball 23 in cooperation with the groove 20
Figure imgb0005
rested. In this working position
Figure imgb0005
the roller 3 of the roller finger follower 2 interacts with the cam track 4b. If, from this starting position, the valve train is to be switched so that the gas exchange valve follows the stroke of the cam track 4c, the actuating pin 15 is lowered by pressurizing the actuating element 11. This then lies on the cylindrical extension 7 and engages Reach the assigned rotational position of the cam in the stroke curve 9, in the further course of which the cam is moved to the left. 3 essentially shows a representation of the working planes, ie the assignment of the lifting crank and cam profile (base circle region 25, 25 'and elevation region 30, 30'). The correct angular assignment of the lifting curves to the cam profile depends on the angular position of the adjusting elements. At the end of the cam 9, the cam 5 has reached its left end position, that of the working position
Figure imgb0002
corresponds, and in which the roller 3 cooperates with the cam track 4c. The stroke curves 9 and 10 are designed in their extension and angular assignment so that the axial displacement only takes place as long as the roller 3 in the base circle region 25 abuts the respective cam tracks 4a to 4c. The cam tracks 4a to 4c are designed in such a way 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 curves 9, 10 or the cylindrical extensions 7, 8, which is angularly shifted depending on the spatial position of the adjusting elements. After reaching the switch position
Figure imgb0002
the actuating element 11 is depressurized so that the actuating pin 11 is moved back into its initial 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 is then still in contact with the respective cylindrical extension, but only comes into engagement with it in the outlet area of the respective stroke curve, so that no adjustment takes place. The respective inlet area 26, 27 and outlet area 28, 29 of the lifting curves 9, 10 merge into the circumferential surface of the cylindrical extensions without a step.

Soll der Nocken aus der Arbeitsstellung

Figure imgb0002
in die mittlere Arbeitsstellung
Figure imgb0005
zurückbewegt werden, wird das Betätigungselement 13 druckbeaufschlagt, so daß der Betätigungsstift 17 am zylindrischen Fortsatz 8 anliegt und bei Erreichen der Grundkreisphase in die Hubkurve 10 eingreift. Durch das Zusammenwirken des Betätigungsstiftes 17 und der Hubkurve 10 wird der Nocken in die mittlere Arbeitsstellung
Figure imgb0005
zurückbewegt.Should the cam out of the working position
Figure imgb0002
in the middle working position
Figure imgb0005
are moved back, the actuating element 13 is pressurized so that the actuating pin 17 rests on the cylindrical extension 8 and when the Base circle phase engages in the cam 10. By the interaction of the actuating pin 17 and the cam 10, the cam is in the middle working position
Figure imgb0005
moved back.

Eine Verschiebung des Nockens aus der mittleren Arbeitsstellung

Figure imgb0005
in die rechte Arbeiststellung
Figure imgb0001
erfolgt durch Beaufschlagung des Betätigungselementes 14, das ebenfalls mit der Hubkurve 10 zusammenwirkt und den Nocken nach rechts bewegt.
Das Zurückstellen des Nockens in die mittlere Arbeitsstellung
Figure imgb0005
erfolgt auf analoge Weise durch Druckbeaufschlagen des Betätigungselementes 12, das mit der Hubkurve 9 zusammenwirkt.A shift of the cam from the middle working position
Figure imgb0005
in the right working position
Figure imgb0001
takes place by acting on the actuating element 14, which also interacts with the cam 10 and moves the cam to the right.
The return of the cam to the middle working position
Figure imgb0005
takes place in an analogous manner by pressurizing the actuating element 12, which interacts with the stroke curve 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)

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 Hubprofil (9, 10), das mit einem Betätigungselement (11 bis 14) zum 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 verschieblich in Eingriff mit dem Hubprofil (9, 10) zu bringen ist.Valve train 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 (4a to 4c) arranged axially one behind the other and is rotatably but axially displaceably guided on the camshaft, and with a lifting profile (9, 10) which interacts with an actuating element (11 to 14) for displacing the cam, characterized in that the lifting profile (9, 10) is formed 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 slidably brought into engagement with the lifting profile (9, 10). Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß das Hubprofil (9, 10) durch eine Kurvenbahn gebildet ist, die in einem benachbart zu den Nockenbahnen angeordneten Zylinderabschnitt (7, 8) ausgebildet ist.Valve drive 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. 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 Hubkurven (9, 10) ausgebildet sind, zwischen denen die Nockenbahnen verlaufen.Valve train according to one of the preceding claims, characterized in that the displaceable cam (5) is provided with three cam tracks (4a to 4c) arranged one behind the other, and in that two lifting curves (9, 10) are formed on the cam, between which the cam tracks run. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß jede Hubkurve (9, 10) in Abhängigkeit von der axialen Schaltstellung des Nockens (5) mit einem von zwei Betätigungsstiften (15, 16; 17, 18) zusammenwirkt, die beim Eingriff in die Hubkurve (9, 19) Axialverschiebungen auslösen.Valve drive according to one of the preceding claims, characterized in that each stroke curve (9, 10), depending on the axial switching position of the cam (5), cooperates with one of two actuating pins (15, 16; 17, 18) which, when engaged in the Actuate the stroke curve (9, 19). 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.Valve train according to one of the preceding claims, characterized in that a latching means (19 to 24) is arranged between the displaceable cam (5) and the camshaft (6), which latches the cam in its respective axial switching position. 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.Valve drive 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).
EP97102494A 1996-03-25 1997-02-15 Valve control of an internal combustion engine Expired - Lifetime EP0798451B1 (en)

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DE102017120145A1 (en) 2017-09-01 2019-03-07 Man Truck & Bus Ag Sliding cam system
US10738665B2 (en) 2017-09-01 2020-08-11 Man Truck & Bus Ag Sliding cam system
KR20190070206A (en) 2017-12-12 2019-06-20 현대자동차주식회사 Variable valve device for engine
CN109915227A (en) * 2017-12-12 2019-06-21 现代自动车株式会社 Variable valve gear for engine
US10458294B2 (en) 2017-12-12 2019-10-29 Hyundai Motor Company Variable valve device for engine
CN109915227B (en) * 2017-12-12 2022-04-08 现代自动车株式会社 Variable valve apparatus for engine

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JPH108928A (en) 1998-01-13
DE59700135D1 (en) 1999-05-27
EP0798451B1 (en) 1999-04-21
DE19611641C1 (en) 1997-06-05
KR100416895B1 (en) 2004-03-31
JP3980699B2 (en) 2007-09-26
KR970065972A (en) 1997-10-13

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