EP2291578A1 - Valve train for gas exchange valves of an internal combustion engine having double-supported cam carriers - Google Patents

Valve train for gas exchange valves of an internal combustion engine having double-supported cam carriers

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Publication number
EP2291578A1
EP2291578A1 EP09765507A EP09765507A EP2291578A1 EP 2291578 A1 EP2291578 A1 EP 2291578A1 EP 09765507 A EP09765507 A EP 09765507A EP 09765507 A EP09765507 A EP 09765507A EP 2291578 A1 EP2291578 A1 EP 2291578A1
Authority
EP
European Patent Office
Prior art keywords
cam
cam carrier
camshaft
valve drive
base camshaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP09765507A
Other languages
German (de)
French (fr)
Other versions
EP2291578B1 (en
Inventor
Michael Hartlieb
Manfred Elbl
Robert Poida
Andreas Ewald
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.)
Audi AG
Original Assignee
Audi AG
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Filing date
Publication date
Application filed by Audi AG filed Critical Audi AG
Publication of EP2291578A1 publication Critical patent/EP2291578A1/en
Application granted granted Critical
Publication of EP2291578B1 publication Critical patent/EP2291578B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a valve drive for gas exchange valves of an internal combustion engine according to the preamble of claims 1 and 12.
  • valve trains are known in which the working cycle can be influenced, for example, to allow a speed-dependent change in the opening times or the stroke of the gas exchange valves.
  • valve train of the type mentioned is already known in which a plurality of cam carrier rotatably and axially displaceably guided on a basic camshaft provided with an external toothing.
  • two axially spaced cam profile groups are provided on the associated cam carrier, each of which has two different cam profiles.
  • the known valve drive has locking devices.
  • each include a pressure element in the form of a detent ball, which is inserted into a radial blind hole of the base camshaft and is pressed by the force of a helical compression spring in the bore radially outwardly against an opposite oblique edge of a detent groove or detent groove.
  • the detent balls act on the associated cam carrier with a radial and an axial force component, of which the latter serves to press the cam carrier against serving as a stop face of a bearing block and thus fix it in a defined axial position.
  • the locking devices are each arranged radially inwardly of a cam profile group in the vicinity of one of the two front ends of each cam carrier.
  • this has a slight misalignment of the cam carrier result.
  • This results in each valve actuation to an audible audible noise, when the opposite, not pressed against the base camshaft Stimende the cam carrier strikes its internal teeth due to a system change in the vicinity of the maximum valve lift against the outer teeth of the basic camshaft.
  • Another cause for the formation of noise in the valve train is that to facilitate the production of the basic camshaft all serving to accommodate the helical compression springs and the locking balls blind holes are aligned parallel to each other and open on the same side of the base camshaft. Due to the different opening times of the gas exchange valves of adjacent cylinders and the angular offset of the lift curves of the cams on adjacent cam carriers required thereby, this results in the radial forces exerted by the locking balls or the pressure elements on the cam carriers having a different angular orientation with respect to the lift curves of the cam carriers which may also be the cause of noise.
  • the parallel alignment of all bores moreover has the disadvantage that the reaction forces exerted by the helical compression springs on the basic camshaft all have the same direction, whereby the base camshaft is supported on one side by the cam carriers and bent in this direction.
  • the invention has the object to counteract a noise in the valve train.
  • an additional pressure element is provided at an axial distance from the pressure element, which is also pressed against an opposite inner peripheral portion of the cam carrier to thereby leading to the noise hitting a non-supported part of the cam carrier during emergence of a Cam on the cooperating with the cam roller cam followers of the associated gas exchange valve to avoid.
  • the two pressure elements of each cam carrier are pressed against the respectively opposite inner peripheral portion of the cam carrier with almost identical pressure forces, which is most easily achieved by using the same or similar springs.
  • the two pressure elements of each cam carrier are preferably pressed with the same orientation against the respective opposite inner peripheral portion of the cam carrier.
  • the orientation of the recesses in the base camshaft serving to receive the pressing elements with respect to the cams of the cam carriers pushed onto the basic camshaft is preferably chosen such that recesses open on the side of the basic camshaft corresponding to the cam tips, i. the crests of the lifting curves of the cam, is approximately opposite, so that the cam carrier are pressed on the side of the cam tips and the lift curves of the cam against the base camshaft.
  • the alignment of the recesses is advantageously chosen so that the longitudinal axes of the recesses formed appropriately as holes between the angular distance run from each other arranged cam tips.
  • the two pressure elements are each in the vicinity of the opposite ends of the cam carrier, i. on opposite sides of an axial center of the cam carrier, wherein they are expediently arranged on both sides of a provided with an external toothing portion of the basic camshaft.
  • the pressing element of the locking device is advantageously offset by a detent recess, while the further pressure element is opposed by a cylindrical peripheral surface of the cam carrier adjoining the internal toothing.
  • a second alternative of the invention and preferred embodiment of the first alternative of the invention provides that the pressure elements of different cam carriers are offset or rotated in the circumferential direction of the base camshaft so that all pressure elements have the same orientation with respect to the lift curves of the cams. This ensures, on the one hand, that the direction of the force attack on all cams or cam carriers is the same, which counteracts a noise.
  • the mutual angular offset of the pressure elements of adjacent cam carriers is preferably 3607n or 2 x 3607n.
  • FIG. 1 shows a partially sectioned side view of a portion of a base camshaft and a cam carrier displaceable on the base camshaft of a valve drive according to the invention for gas exchange valves of an internal combustion engine;
  • Fig. 2 a side view of the entire basic camshaft without cam carrier, i. before mounting on the basic camshaft;
  • 3a to 3d cross-sectional views of the basic camshaft along the lines a-a, b-b, c-c and d-d of Fig. 2 after mounting the cam carrier on the base camshaft and the interaction thereof with roller cam followers of gas exchange valves of four cylinders arranged in series with the same valve.
  • valve drive 1 In the case of the valve drive 1 only partially illustrated in the drawing for pairs of intake valves 2 of four cylinders of a straight-line engine, the stroke and the opening times of the two intake valves 2 of each cylinder can be adjusted.
  • valve drive 1 comprises a rotatably mounted basic camshaft 3 and four cam carriers 4, mounted rotatably and axially displaceably on the base camshaft 3, one of which is shown enlarged in longitudinal section in FIG. 1 and two actuators 5 for displacing each cam carrier 4 between two defined axial displacement positions.
  • the cam carrier 4 have at their outer periphery in each case two axially spaced cam pairs 6, each of which consists of two cams 7, 8. As best shown in FIGS. 1 and 3, each of the pair of cams 6 cooperates with a roller 9 of a pivotally mounted roller cam 10 of the associated inlet valve 2.
  • the rollers 9 as required with one of the two cams 7, 8 of a pair of cams. 6 be brought into abutting contact, so that they move over a stroke contour 11 of the cam 7, 8 during each revolution of the base camshaft 3 once, the roller rocker arm 10 is pivoted by opening the valve 2.
  • one of the two actuators 5 is actuated in each case in order to extend a driver pin 12 of the actuator 5 during one revolution of the cam carrier 4 and thereby engage in an opposite helical groove 13 on the adjacent end of the cam carrier 4.
  • the displacement of the cam carrier 4 always takes place when base circle sections 14 of the cams 7, 8 of both pairs of cams 6 rest against the rollers 9 of the cam followers 10.
  • each cam carrier 4 In order to guide the tubular cam carrier 4 in a rotationally fixed and axially displaceable manner on the base camshaft 3, the latter is provided within each cam carrier 4 at its outer circumference in sections with an external toothing 15 which meshes with a complementary internal toothing 16 on the inner circumference of the associated cam carrier 4. As best shown in Fig. 2, portions 17 are provided with a cylindrical peripheral surface between adjacent, provided with an external toothing portions, over which the external teeth 15 protrudes.
  • Each cam carrier 4 has between the two pairs of cams 5, 6 a cylindrical portion 18 which is mounted in a fixedly mounted in the cylinder head housing slide bearing 19, as best shown in Fig. 1.
  • the sliding bearing 19 has two opposite end faces 20, 21, which serve in each of the two displacement positions as a stop for an opposite end face 22, 23 of the cam 18 adjacent to the portion 18 of each cam pair 6, to a defined axial position of the cam carrier 4 to adjust.
  • a locking device 24 is provided at a front end of each cam carrier 4.
  • the locking device comprises a radial blind hole 25 in the base camshaft 3, in which a locking ball 26 is guided radially movable.
  • a helical compression spring 27 is used, which presses the locking ball 26 radially outwardly against an inclined groove flank 28 in one of two recessed in an inner circumferential portion of the cam carrier 4 recessed grooves 29 and thereby the cam carrier 4 against one of the stop surfaces 20, 21 expresses as described in detail in the aforementioned DE 10 2004 011 586 A1 of the Applicant.
  • a blind hole 30 parallel to the blind bore 25 is arranged on the opposite end face of the cam carrier 4, in which also a radially movable ball 31 radially outwardly by the force of a helical compression spring 32 is pressed against an opposite inner peripheral portion of the cam carrier 4.
  • the inner peripheral portion of the cam carrier has a cylindrical surface 33, in which no latching grooves 29 are recessed.
  • each cam carrier 4 open on the same side of the base camshaft 3, while the two helical compression springs 28, 32 have the same dimensions, so that of them on the balls 26, 31 applied forces have the same direction and almost the same amount.
  • the pairs of blind bores 25, 30 for the four cam carriers 4 mounted on the base camshaft 3 are aligned such that they each have an angle corresponding to the firing order, in the exemplary embodiment shown in the drawing 90.degree 180 °, with the blind bores 25, 30 for the or the adjacent cam carrier 4, this angle also corresponds to the angular offset with which the adjacent cam carrier 4 are pushed onto the basic camshaft 3 for driving the intake valves 2 of successive cylinders of the cylinder row. It is thus achieved that the balls 26, 31 are arranged in the same position with respect to the lifting curves 11 of the cams 7, 8 in all the cam carriers 4, as shown in FIGS.
  • the drive of the basic camshaft 3 takes place via a sprocket wheel 34 (FIG. 2) of a chain drive (not shown), which is arranged in the vicinity of its one front end and connected in a rotationally fixed manner to the base camshaft 3.

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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)

Abstract

The invention relates to a valve train (1) for gas exchange valves (2) of an internal combustion engine, having a base camshaft (3), a plurality of cam carriers (4) arranged on the base camshaft (3) in a rotationally fixed and axially displaceable way, and locking devices (24) for retaining the cam carriers (4) in defined displacement positions along the base camshaft (3). The locking devices (24) each comprise a pressing element (26), which is inserted into a recess (25) of the base camshaft (3) and pressed in the radial direction of the base camshaft (3) against an opposing inner circumferential section of the cam carrier (4). In order to counteract noise development in the valve train, according to a first variant of the invention, a further pressing element (31) is provided at an axial distance to the pressing element (26) and is pressed against an opposing inner circumferential section (33) of the cam carrier (4). According to a second alternative or additional variant of the invention, the pressing elements (26, 31) of different cam carriers (4) are offset from each other in the circumferential direction of the base camshaft (3).

Description

Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit doppelt abgestützten Nockenträgern Valve drive for gas exchange valves of an internal combustion engine with double-supported cam carriers
Die Erfindung betrifft einen Ventiltrieb für Gaswechselventile einer Brennkraftmaschine gemäß dem Oberbegriff der Ansprüche 1 und 12.The invention relates to a valve drive for gas exchange valves of an internal combustion engine according to the preamble of claims 1 and 12.
Zur Verbesserung der thermodynamischen Eigenschaften von Brennkraftmaschinen sind Ventiltriebe bekannt, bei denen das Arbeitsspiel beeinflusst werden kann, um beispielsweise eine drehzahlabhängige Veränderung der Öffnungszeiten oder des Hubs der Gaswechselventile zu ermöglichen.To improve the thermodynamic properties of internal combustion engines valve trains are known in which the working cycle can be influenced, for example, to allow a speed-dependent change in the opening times or the stroke of the gas exchange valves.
Aus der DE 10 2004 011 586 A1 der Anmelderin ist bereits ein Ventiltrieb der eingangs genannten Art bekannt, bei dem auf einer mit einer Außenverzahnung versehenen Grundnockenwelle mehrere Nockenträger mit einer komplementären Innenverzahnung drehfest und axial verschiebbar geführt sind. Zur Betätigung von zwei Gaswechselventilen eines Zylinders sind auf dem zugehörigen Nockenträger zwei im axialen Abstand voneinander angeordnete Nockenprofilgruppen vorgesehen, von denen jede zwei verschiedene Nockenprofile aufweist. Durch axiale Verschiebung der Nockenträger auf der Grundnockenwelle zwischen zwei definierten Verschiebestellungen lässt sich jeweils eines der beiden Nockenprofile jeder Nockenprofilgruppe mit einer Rolle eines Rollenschlepphebels des zugehörigen Gaswechselventils in Anlagekontakt bringen. Um die Nockenträger in den beiden Verschiebestellungen in definierten axialen Positionen zu fixieren, weist der bekannte Ventiltrieb Arretiervorrichtungen auf. Diese umfassen jeweils ein Andruckelement in Form einer Rastkugel, die in eine radiale Sacklochbohrung der Grundnockenwelle eingesetzt ist und durch die Kraft einer Schraubendruckfeder in der Bohrung radial auswärts gegen eine gegenüberliegende schräge Flanke einer Rastrille oder Rastnut angepresst wird. Die Rastkugeln wirken dadurch auf den zugehörigen Nockenträger mit einer radialen und einer axialen Kraftkomponente ein, von denen die letztere dazu dient, den Nockenträger gegen eine als Anschlag dienende Stirnfläche eines Lagerbocks zu drücken und ihn damit in einer definierten axialen Stellung zu fixieren.From DE 10 2004 011 586 A1 of the Applicant already a valve train of the type mentioned is already known in which a plurality of cam carrier rotatably and axially displaceably guided on a basic camshaft provided with an external toothing. To actuate two gas exchange valves of a cylinder two axially spaced cam profile groups are provided on the associated cam carrier, each of which has two different cam profiles. By axial displacement of the cam carrier on the base camshaft between two defined displacement positions, one of the two cam profiles of each cam profile group can be brought into abutting contact with a roller of a roller cam follower of the associated gas exchange valve. In order to fix the cam carrier in the two displacement positions in defined axial positions, the known valve drive has locking devices. These each include a pressure element in the form of a detent ball, which is inserted into a radial blind hole of the base camshaft and is pressed by the force of a helical compression spring in the bore radially outwardly against an opposite oblique edge of a detent groove or detent groove. The detent balls act on the associated cam carrier with a radial and an axial force component, of which the latter serves to press the cam carrier against serving as a stop face of a bearing block and thus fix it in a defined axial position.
Bei dem bekannten Ventiltrieb sind die Arretiervorrichtungen jeweils radial einwärts von einer Nockenprofilgruppe in der Nähe von einem der beiden Stirnenden jedes Nockenträgers angeordnet. In Verbindung mit dem zur Verschiebung des Nockenträgers erforderlichen radialen Spiel zwischen der Außenverzahnung der Grundnockenwelle und der Innenverzahnung des Nockenträgers hat dies eine leichte Schiefstellung des Nockenträgers zur Folge. Dies wiederum führt bei jeder Ventilbetätigung zu einem akustisch hörbaren Geräusch, wenn am entgegengesetzten, nicht gegen die Grundnockenwelle ange- pressten Stimende des Nockenträgers dessen Innenverzahnung infolge eines Anlagewechsels in der Nähe des maximalen Ventilhubs gegen die Außenverzahnung der Grundnockenwelle anschlägt.In the known valve train, the locking devices are each arranged radially inwardly of a cam profile group in the vicinity of one of the two front ends of each cam carrier. In conjunction with the required for the displacement of the cam carrier radial clearance between the outer teeth of the base camshaft and the Internal toothing of the cam carrier, this has a slight misalignment of the cam carrier result. This in turn results in each valve actuation to an audible audible noise, when the opposite, not pressed against the base camshaft Stimende the cam carrier strikes its internal teeth due to a system change in the vicinity of the maximum valve lift against the outer teeth of the basic camshaft.
Eine weitere Ursache für die Entstehung von Geräuschen im Ventiltrieb besteht darin, dass zur Erleichterung der Herstellung der Grundnockenwelle sämtliche der zur Aufnahme der Schraubendruckfedern und der Arretierkugeln dienenden Sacklochbohrungen parallel zueinander ausgerichtet sind und an derselben Seite der Grundnockenwelle münden. Infolge der unterschiedlichen Öffnungszeiten der Gaswechselventile benachbarter Zylinder und des dadurch erforderlichen Winkelversatzes der Hubkurven der Nocken auf benachbarten Nockenträgern führt dies jedoch dazu, dass die von den Arretierkugeln bzw. den Andruckelementen auf die Nockenträger ausgeübten radialen Kräfte in Bezug zu den Hubkurven der Nockenträger eine unterschiedliche Winkelausrichtung besitzen, welche ebenfalls die Ursache für Geräusche sein kann. Die parallele Ausrichtung sämtlicher Bohrungen hat darüber hinaus auch noch den Nachteil, dass die von den Schraubendruckfedern auf die Grundnockenwelle ausgeübten Reaktionskräfte sämtlich dieselbe Richtung besitzen, wodurch die Grundnockenwelle über die Nockenträger einseitig abgestützt und in dieser Richtung durchgebogen wird.Another cause for the formation of noise in the valve train is that to facilitate the production of the basic camshaft all serving to accommodate the helical compression springs and the locking balls blind holes are aligned parallel to each other and open on the same side of the base camshaft. Due to the different opening times of the gas exchange valves of adjacent cylinders and the angular offset of the lift curves of the cams on adjacent cam carriers required thereby, this results in the radial forces exerted by the locking balls or the pressure elements on the cam carriers having a different angular orientation with respect to the lift curves of the cam carriers which may also be the cause of noise. The parallel alignment of all bores moreover has the disadvantage that the reaction forces exerted by the helical compression springs on the basic camshaft all have the same direction, whereby the base camshaft is supported on one side by the cam carriers and bent in this direction.
Ausgehend hiervon liegt der Erfindung die Aufgabe zugrunde, einer Geräuschentwicklung im Ventiltrieb entgegenzuwirken.Proceeding from this, the invention has the object to counteract a noise in the valve train.
Diese Aufgabe wird gemäß einer ersten Erfindungsalternative dadurch gelöst, dass im axialen Abstand vom Andruckelement ein weiteres Andruckelement vorgesehen ist, das ebenfalls gegen einen gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers angepresst wird, um dadurch ein zur Geräuschentstehung führendes Schlagen eines nicht abgestützten Teils des Nockenträgers beim Auflaufen eines Nockens auf den mit dem Nocken zusammenwirkenden Rollenschlepphebel des zugehörigen Gaswechselventils zu vermeiden.This object is achieved according to a first alternative of the invention in that an additional pressure element is provided at an axial distance from the pressure element, which is also pressed against an opposite inner peripheral portion of the cam carrier to thereby leading to the noise hitting a non-supported part of the cam carrier during emergence of a Cam on the cooperating with the cam roller cam followers of the associated gas exchange valve to avoid.
Gemäß einer bevorzugten Ausgestaltung dieser Erfindungsvariante werden die beiden Andruckelemente jedes Nockenträgers mit nahezu gleichen Andruckkräften gegen den jeweils gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers angepresst, was am einfachsten durch Verwendung gleicher oder ähnlicher Federn erreicht werden kann.According to a preferred embodiment of this variant of the invention, the two pressure elements of each cam carrier are pressed against the respectively opposite inner peripheral portion of the cam carrier with almost identical pressure forces, which is most easily achieved by using the same or similar springs.
Um eine Fluchtung der Längsachse des Nockenträgers mit der Drehachse der Grundnockenwellen zu gewährleisten und dadurch eine Schiefstellung des Nockenträgers zu vermeiden, werden die beiden Andruckelemente jedes Nockenträgers bevorzugt mit derselben Ausrichtung gegen den jeweils gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers angepresst.In order to ensure alignment of the longitudinal axis of the cam carrier with the axis of rotation of the base camshaft and thereby avoid skewing of the cam carrier, the two pressure elements of each cam carrier are preferably pressed with the same orientation against the respective opposite inner peripheral portion of the cam carrier.
Die Ausrichtung der zur Aufnahme der Andruckelemente dienenden Ausnehmungen in der Grundnockenwelle in Bezug zu den Nocken der auf die Grundnockenwelle aufgeschobenen Nockenträger wird vorzugsweise so gewählt, dass Ausnehmungen auf derjenigen Seite der Grundnockenwelle münden, die zu den Nockenspitzen, d.h. den Scheiteln der Hubkurven der Nocken, etwa entgegengesetzt ist, so dass die Nockenträger auf der Seite der Nockenspitzen bzw. der Hubkurven der Nocken gegen die Grundnockenwelle angepresst werden.The orientation of the recesses in the base camshaft serving to receive the pressing elements with respect to the cams of the cam carriers pushed onto the basic camshaft is preferably chosen such that recesses open on the side of the basic camshaft corresponding to the cam tips, i. the crests of the lifting curves of the cam, is approximately opposite, so that the cam carrier are pressed on the side of the cam tips and the lift curves of the cam against the base camshaft.
Dort, wo die Nockenträger zwei Paare von Nocken tragen und die Nockenspitzen jedes Nockenpaars in Umfangsrichtung der Grundnockenwelle und der Nockenträger einen gewissen Winkelabstand voneinander aufweisen, wird die Ausrichtung der Ausnehmungen vorteilhaft so gewählt, dass die Längsachsen der zweckmäßig als Bohrungen ausgebildeten Ausnehmungen zwischen den im Winkelabstand voneinander angeordneten Nockenspitzen hindurch verlaufen.Where the cam carrier carry two pairs of cams and the cam tips of each pair of cams in the circumferential direction of the base camshaft and the cam carrier have a certain angular distance from each other, the alignment of the recesses is advantageously chosen so that the longitudinal axes of the recesses formed appropriately as holes between the angular distance run from each other arranged cam tips.
Vorzugsweise befinden sich die beiden Andruckelemente jeweils in der Nähe der entgegengesetzten Stirnenden des Nockenträgers, d.h. auf entgegengesetzten Seiten einer axialen Mitte des Nockenträgers, wobei sie zweckmäßig beiderseits von einem mit einer Außenverzahnung versehenen Abschnitt der Grundnockenwelle angeordnet sind. Vorteilhaft liegt dabei dem Andruckelement der Arretiervorrichtung eine Rastvertiefung gegenüber, während dem weiteren Andruckelement eine an die Innenverzahnung angrenzende zylindrische Umfangsfläche des Nockenträgers gegenüberliegt.Preferably, the two pressure elements are each in the vicinity of the opposite ends of the cam carrier, i. on opposite sides of an axial center of the cam carrier, wherein they are expediently arranged on both sides of a provided with an external toothing portion of the basic camshaft. In this case, the pressing element of the locking device is advantageously offset by a detent recess, while the further pressure element is opposed by a cylindrical peripheral surface of the cam carrier adjoining the internal toothing.
Eine zweite Erfindungsalternative und bevorzugte Ausgestaltung der ersten Erfindungsalternative sieht vor, dass die Andruckelemente verschiedener Nockenträger in Umfangsrichtung der Grundnockenwelle so versetzt oder verdreht sind, dass alle Andruckelemente in Bezug zu den Hubkurven der Nocken dieselbe Ausrichtung besitzen. Dadurch wird zum einen gewährleistet, dass die Richtung des Kraftangriffs bei allen Nocken bzw. Nockenträgern dieselbe ist, was einer Geräuschentwicklung entgegenwirkt. Bei einer Anzahl von n Nockenträgern auf der Grundnockenwelle beträgt der gegenseitige Winkelversatz der Andruckelemente benachbarter Nockenträger vorzugsweise 3607n oder 2 x 3607n. Dadurch stützt sich die Grundnockenwelle gleichmäßig in allen Richtungen über die Nockenträger in den Lagern ab und bleibt daher gerade.A second alternative of the invention and preferred embodiment of the first alternative of the invention provides that the pressure elements of different cam carriers are offset or rotated in the circumferential direction of the base camshaft so that all pressure elements have the same orientation with respect to the lift curves of the cams. This ensures, on the one hand, that the direction of the force attack on all cams or cam carriers is the same, which counteracts a noise. With a number of n cam carriers on the base camshaft, the mutual angular offset of the pressure elements of adjacent cam carriers is preferably 3607n or 2 x 3607n. As a result, the basic camshaft is supported evenly in all directions via the cam carriers in the bearings and therefore remains straight.
Im folgenden wird die Erfindung anhand eines in der Zeichnung dargestellten Ausführungsbeispiels näher erläutert. Es zeigen:In the following the invention will be explained in more detail with reference to an embodiment shown in the drawing. Show it:
Fig. 1 : eine teilweise geschnittene Seitenansicht eines Abschnitts einer Grundnockenwelle und eines auf der Grundnockenwelle verschiebbaren Nockenträgers eines erfindungsgemäßen Ventiltriebs für Gaswechselventile einer Brennkraftmaschine;1 shows a partially sectioned side view of a portion of a base camshaft and a cam carrier displaceable on the base camshaft of a valve drive according to the invention for gas exchange valves of an internal combustion engine;
Fig. 2: eine Seitenansicht der gesamten Grundnockenwelle ohne Nockenträger, d.h. vor deren Montage auf der Grundnockenwelle;Fig. 2: a side view of the entire basic camshaft without cam carrier, i. before mounting on the basic camshaft;
Fig. 3a bis 3d: Querschnittsansichten der Grundnockenwelle entlang der Linien a-a, b-b, c-c bzw. d-d der Fig. 2 nach der Montage der Nockenträger auf der Grundnockenwelle und beim Zusammenwirken derselben mit Rollenschlepphebeln von Gaswechselventilen von vier in Reihe angeordneten Zylindern bei gleichem Ventilhub.3a to 3d: cross-sectional views of the basic camshaft along the lines a-a, b-b, c-c and d-d of Fig. 2 after mounting the cam carrier on the base camshaft and the interaction thereof with roller cam followers of gas exchange valves of four cylinders arranged in series with the same valve.
Bei dem in der Zeichnung nur teilweise dargestellten Ventiltrieb 1 für Paare von Einlassventilen 2 von vier Zylindern eines Reihenmotors lassen sich der Hub und die Öffnungszeiten der beiden Einlassventile 2 jedes Zylinders verstellen.In the case of the valve drive 1 only partially illustrated in the drawing for pairs of intake valves 2 of four cylinders of a straight-line engine, the stroke and the opening times of the two intake valves 2 of each cylinder can be adjusted.
Der Ventiltrieb 1 umfasst dazu eine drehbar gelagerte Grundnockenwelle 3 und vier drehfest und axial verschiebbar auf der Grundnockenwelle 3 montierte Nockenträger 4, von denen in Fig. 1 einer im Längsschnitt vergrößert dargestellt ist, sowie zwei Aktuato- ren 5 zum Verschieben jedes Nockenträgers 4 zwischen zwei definierten axialen Verschiebestellungen.For this purpose, the valve drive 1 comprises a rotatably mounted basic camshaft 3 and four cam carriers 4, mounted rotatably and axially displaceably on the base camshaft 3, one of which is shown enlarged in longitudinal section in FIG. 1 and two actuators 5 for displacing each cam carrier 4 between two defined axial displacement positions.
Die Nockenträger 4 weisen an ihrem äußeren Umfang jeweils zwei im axialen Abstand voneinander angeordnete Nockenpaare 6 auf, von denen jedes aus zwei Nocken 7, 8 besteht. Wie am besten in Fig. 1 und 3 dargestellt, wirkt jedes der beiden Nockenpaare 6 mit einer Rolle 9 eines schwenkbar gelagerten Rollenschlepphebels 10 des zugehörigen Einlassventils 2 zusammen. Durch eine axiale Verschiebung eines Nockenträgers 4 können die Rollen 9 nach Bedarf mit einem der beiden Nocken 7, 8 eines Nockenpaars 6 in Anlagekontakt gebracht werden, so dass sie sich während jeder Umdrehung der Grundnockenwelle 3 einmal über eine Hubkontur 11 des Nockens 7, 8 hinwegbewegen, wobei der Rollenschlepphebel 10 unter Öffnen des Ventils 2 verschwenkt wird. Durch eine unterschiedliche Höhe, Form und/oder Position der Hubkonturen 11 der beiden Nocken 7, 8 können der Hub und die Öffnungszeit jedes Ventils 2 in Abhängigkeit von der jeweiligen Verschiebestellung des Nockenträgers 4 aber unabhängig vom Hub und der Öffnungszeit der Ventile 2 der anderen Zylinder zum Beispiel drehzahlabhängig verändert werden.The cam carrier 4 have at their outer periphery in each case two axially spaced cam pairs 6, each of which consists of two cams 7, 8. As best shown in FIGS. 1 and 3, each of the pair of cams 6 cooperates with a roller 9 of a pivotally mounted roller cam 10 of the associated inlet valve 2. By an axial displacement of a cam carrier 4, the rollers 9 as required with one of the two cams 7, 8 of a pair of cams. 6 be brought into abutting contact, so that they move over a stroke contour 11 of the cam 7, 8 during each revolution of the base camshaft 3 once, the roller rocker arm 10 is pivoted by opening the valve 2. By a different height, shape and / or position of Hubkonturen 11 of the two cams 7, 8, the stroke and the opening time of each valve 2 in response to the respective displacement position of the cam carrier 4 but independent of the stroke and the opening time of the valves 2 of the other cylinder be changed depending on the speed, for example.
Zur Verschiebung der Nockenträger 4 wird jeweils einer der beiden Aktuatoren 5 betätigt, um einen Mitnehmerstift 12 des Aktuators 5 während einer Umdrehung des Nockenträgers 4 auszufahren und dabei in eine gegenüberliegende schraubenförmige Nut 13 am benachbarten Stimende des Nockenträgers 4 einzuspuren. Die Verschiebung des Nockenträgers 4 erfolgt immer dann, wenn Grundkreisabschnitte 14 der Nocken 7, 8 beider Nockenpaare 6 gegen die Rollen 9 der Schlepphebel 10 anliegen.To displace the cam carrier 4, one of the two actuators 5 is actuated in each case in order to extend a driver pin 12 of the actuator 5 during one revolution of the cam carrier 4 and thereby engage in an opposite helical groove 13 on the adjacent end of the cam carrier 4. The displacement of the cam carrier 4 always takes place when base circle sections 14 of the cams 7, 8 of both pairs of cams 6 rest against the rollers 9 of the cam followers 10.
Um die röhrenförmigen Nockenträger 4 drehfest und axial verschiebbar auf der Grundnockenwelle 3 zu führen, ist diese letztere innerhalb von jedem Nockenträger 4 an ihrem äußeren Umfang abschnittsweise mit einer Außenverzahnung 15 versehen, die mit einer komplementären Innenverzahnung 16 am inneren Umfang des zugehörigen Nockenträgers 4 kämmt. Wie am besten in Fig. 2 dargestellt, sind zwischen benachbarten, mit einer Außenverzahnung 15 versehenen Abschnitten jeweils Abschnitte 17 mit einer zylindrischen Umfangsfläche vorgesehen, über welche die Außenverzahnung 15 übersteht.In order to guide the tubular cam carrier 4 in a rotationally fixed and axially displaceable manner on the base camshaft 3, the latter is provided within each cam carrier 4 at its outer circumference in sections with an external toothing 15 which meshes with a complementary internal toothing 16 on the inner circumference of the associated cam carrier 4. As best shown in Fig. 2, portions 17 are provided with a cylindrical peripheral surface between adjacent, provided with an external toothing portions, over which the external teeth 15 protrudes.
Jeder Nockenträger 4 weist zwischen den beiden Nockenpaaren 5, 6 einen zylindrischen Abschnitt 18 auf, der in einem ortsfest im Zylinderkopfgehäuse montierten Gleitlager 19 gelagert ist, wie am besten in Fig. 1 dargestellt. Das Gleitlager 19 weist zwei entgegengesetzte Stirnflächen 20, 21 auf, die in den beiden Verschiebestellungen jeweils als Anschlag für eine gegenüberliegende Stirnfläche 22, 23 des an den Abschnitt 18 angrenzenden Nockens 8 bzw. 7 jedes Nockenpaars 6 dienen, um eine definierte axiale Position des Nockenträgers 4 einzustellen.Each cam carrier 4 has between the two pairs of cams 5, 6 a cylindrical portion 18 which is mounted in a fixedly mounted in the cylinder head housing slide bearing 19, as best shown in Fig. 1. The sliding bearing 19 has two opposite end faces 20, 21, which serve in each of the two displacement positions as a stop for an opposite end face 22, 23 of the cam 18 adjacent to the portion 18 of each cam pair 6, to a defined axial position of the cam carrier 4 to adjust.
Um die Nockenträger 4 in ihren jeweiligen Verschiebestellungen gegen die entsprechende Stirnfläche 20 oder 21 des Gleitlagers 19 anliegend festzuhalten, ist an einem Stirnende jedes Nockenträgers 4 eine Arretiervorrichtung 24 vorgesehen. Die Arretiervorrichtung umfasst eine radiale Sacklochbohrung 25 in der Grundnockenwelle 3, in der eine Arretierkugel 26 radial beweglich geführt ist. Zwischen die Arretierkugel 26 und ei- nem Boden der Sacklochbohrung 25 ist eine Schraubendruckfeder 27 eingesetzt, welche die Arretierkugel 26 radial nach außen gegen eine schräge Nutflanke 28 in einer von zwei in einem gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers 4 ausgesparten Rastnuten 29 presst und dadurch den Nockenträger 4 gegen eine der Anschlagflächen 20, 21 drückt, wie dies in der eingangs genannten DE 10 2004 011 586 A1 der Anmelderin ausführlich beschrieben ist.In order to firmly hold the cam carrier 4 in their respective displacement positions against the corresponding end face 20 or 21 of the sliding bearing 19, a locking device 24 is provided at a front end of each cam carrier 4. The locking device comprises a radial blind hole 25 in the base camshaft 3, in which a locking ball 26 is guided radially movable. Between the locking ball 26 and an nem bottom of the blind hole 25 is a helical compression spring 27 is used, which presses the locking ball 26 radially outwardly against an inclined groove flank 28 in one of two recessed in an inner circumferential portion of the cam carrier 4 recessed grooves 29 and thereby the cam carrier 4 against one of the stop surfaces 20, 21 expresses as described in detail in the aforementioned DE 10 2004 011 586 A1 of the Applicant.
Um zu vermeiden, dass der Nockenträger 4 auf der Grundnockenwelle 3 eine leichte Schieflage einnimmt, ist am entgegengesetzten Stirnende des Nockenträgers 4 eine zur Sacklochbohrung 25 parallele Sacklochbohrung 30 angeordnet, in der ebenfalls eine radial bewegliche Kugel 31 durch die Kraft einer Schraubendruckfeder 32 radial nach außen gegen einen gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers 4 angepresst wird. Anders als im Bereich der Arretiervorrichtung 24 weist jedoch der innere Umfangsabschnitt des Nockenträgers eine zylindrische Oberfläche 33 auf, in der keine Rastnuten 29 ausgespart sind.In order to avoid that the cam carrier 4 assumes a slight imbalance on the base camshaft 3, a blind hole 30 parallel to the blind bore 25 is arranged on the opposite end face of the cam carrier 4, in which also a radially movable ball 31 radially outwardly by the force of a helical compression spring 32 is pressed against an opposite inner peripheral portion of the cam carrier 4. Unlike in the region of the locking device 24, however, the inner peripheral portion of the cam carrier has a cylindrical surface 33, in which no latching grooves 29 are recessed.
Wie am besten in Fig. 1 und 2 dargestellt, münden die beiden Sacklochbohrungen 25, 30 im Inneren jedes Nockenträgers 4 an derselben Seite der Grundnockenwelle 3, während die beiden Schraubendruckfedern 28, 32 die gleiche Dimensionierung aufweisen, so dass die von ihnen auf die Kugeln 26, 31 ausgeübten Kräfte die gleiche Richtung und nahezu den gleichen Betrag besitzen.As best shown in FIGS. 1 and 2, the two blind bores 25, 30 in the interior of each cam carrier 4 open on the same side of the base camshaft 3, while the two helical compression springs 28, 32 have the same dimensions, so that of them on the balls 26, 31 applied forces have the same direction and almost the same amount.
Wie am besten in Fig. 2 dargestellt, sind jedoch die Paare von Sacklochbohrungen 25, 30 für die vier auf der Grundnockenwelle 3 montierten Nockenträger 4 so ausgerichtet, dass sie jeweils einen der Zündfolge entsprechenden Winkel, bei dem in der Zeichnung dargestellten Ausführungsbeispiel 90° bzw. 180°, mit den Sacklochbohrungen 25, 30 für den oder die benachbarten Nockenträger 4 einschließen, wobei dieser Winkel auch dem Winkelversatz entspricht, mit dem die benachbarten Nockenträger 4 zur Ansteuerung der Einlassventile 2 aufeinanderfolgender Zylinder der ι Zylinderreihe auf die Grundnockenwelle 3 aufgeschoben werden. Dadurch wird erreicht, dass die Kugeln 26, 31 bei sämtlichen Nockenträgern 4 in derselben Position in Bezug zu den Hubkurven 11 der Nocken 7, 8 angeordnet sind, wie in den Figuren 3a bis 3d dargestellt, so dass die Richtungen der von den Schraubendruckfedern 27, 32 über die Kugeln 26, 31 in die Nockenträger 4 eingeleiteten Kräfte bei sämtlichen Nockenträgern 4 in Bezug zu den Hubkurven 11 dieselbe Ausrichtung besitzen. Dadurch lässt sich beim Auflaufen der Hubkurven 11 auf die Rollen 9 der Rollenschlepphebel 10 die Entstehung von Geräuschen vermeiden. Indem man jeweils eines der vier Paare von Sacklochbohrungen 25, 30 unter einem Winkel von 0°, 90°, 180° und 270° anordnet, wird zum anderen die Grundnockenwelle 3 über die vier Nockenträger 4 gleichmäßig in den die Nockenträger 4 umgebenden Gleitlagern 19 abgestützt, wodurch eine einseitige Durchbiegung vermieden wird.As best shown in FIG. 2, however, the pairs of blind bores 25, 30 for the four cam carriers 4 mounted on the base camshaft 3 are aligned such that they each have an angle corresponding to the firing order, in the exemplary embodiment shown in the drawing 90.degree 180 °, with the blind bores 25, 30 for the or the adjacent cam carrier 4, this angle also corresponds to the angular offset with which the adjacent cam carrier 4 are pushed onto the basic camshaft 3 for driving the intake valves 2 of successive cylinders of the cylinder row. It is thus achieved that the balls 26, 31 are arranged in the same position with respect to the lifting curves 11 of the cams 7, 8 in all the cam carriers 4, as shown in FIGS. 3a to 3d, so that the directions of the compression springs 27, 32 on the balls 26, 31 in the cam carrier 4 introduced forces in all cam carriers 4 with respect to the lifting cam 11 have the same orientation. As a result, the emergence of the noises 11 can be avoided when the lifting cam 11 comes to rest on the rollers 9 of the roller cam followers 10. By arranging each one of the four pairs of blind holes 25, 30 at an angle of 0 °, 90 °, 180 ° and 270 °, on the other hand, the base camshaft 3 via the four cam carrier 4 evenly supported in the cam supports 4 surrounding bearings 19 , whereby a one-sided deflection is avoided.
Der Antrieb der Grundnockenwelle 3 erfolgt über ein in der Nähe von ihrem einen Stirnende angeordneten, drehfest mit der Grundnockenwelle 3 verbundenen Kettenrad 34 (Fig. 2) eines Kettentriebs (nicht dargestellt). The drive of the basic camshaft 3 takes place via a sprocket wheel 34 (FIG. 2) of a chain drive (not shown), which is arranged in the vicinity of its one front end and connected in a rotationally fixed manner to the base camshaft 3.
BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS
Ventiltrieb Einlassventil Grundnockenwelle Nockenträger Aktuator Nockenpaar Nocken Nocken Rolle Rollenschlepphebel Hubkurve Mitnehmerstift schraubenförmige Nut Grundkreisabschnitt Außenverzahnung Grundnockenwelle Innenverzahnung Nockenträger zylindrische Abschnitte Grundnockenwelle zylindrische Mittelabschnitte Nockenträger Gleitlager Stirnfläche Gleitlager Stirnfläche Gleitlager Stirnfläche Nocken Stirnfläche Nocken Arretiervorrichtung Sacklochbohrung Arretierkugel Schraubendruckfeder Nutflanke Nuten Sacklochbohrung Kugel Schraubendruckfeder zylindrische Oberfläche Zahnscheibe Valve drive Intake valve Basic camshaft Cam carrier Actuator Cam pair Cam Camshaft Roller Cam follower Hub cam Follower pin Helical groove Base circle section External toothing Basic camshaft Internal toothing Cam carrier Cylindrical sections Basic camshaft Cylindrical middle sections Cam carrier Slide bearing Face Sliding bearing Face Sliding bearing Face Cam End face Cam Locking device Blind hole Locking ball Helical compression spring Grooved flute Grooves Blind hole Ball Helical compression spring Cylindrical surface Pulley

Claims

PAT E N TA N S P R Ü C H E PAT EN TA NSPR O CHE
1. Ventiltrieb für Gaswechselventile einer Brennkraftmaschine, mit einer Grundnockenwelle, mehreren drehfest und axial verschiebbar auf der Grundnockenwelle angeordneten Nockenträgern, sowie Arretiervorrichtungen zum Festhalten der Nockenträger in definierten Verschiebestellungen entlang der Grundnockenwelle, wobei die Arretiervorrichtungen jeweils ein Andruckelement umfassen, das in eine Ausnehmung der Grundnockenwelle eingesetzt ist und in radialer Richtung der Grundnockenwelle gegen einen gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers angepresst wird, dadurch gekennzeichnet, dass im axialen Abstand vom Andruckelement (26) ein weiteres Andruckelement (31) vorgesehen ist, das gegen einen gegenüberliegenden inneren Umfangsabschnitt (33) des Nockenträgers (4) angepresst wird.1. Valve drive for gas exchange valves of an internal combustion engine, with a basic camshaft, a plurality of rotatably and axially displaceably arranged on the base camshaft cam carriers, and locking devices for holding the cam carrier in defined displacement positions along the base camshaft, wherein the locking devices each comprise a pressure element in a recess of the base camshaft is inserted and is pressed in the radial direction of the base camshaft against an opposite inner peripheral portion of the cam carrier, characterized in that at an axial distance from the pressure element (26), a further pressure element (31) is provided, against an opposite inner peripheral portion (33) of the cam carrier (4) is pressed.
2. Ventiltrieb nach Anspruch 1 , dadurch gekennzeichnet, dass die beiden Andruckelemente (26, 31) jedes Nockenträgers (4) mit nahezu gleichen Andruckkräften gegen den jeweils gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers (4) angepresst werden.2. Valve drive according to claim 1, characterized in that the two pressure elements (26, 31) of each cam carrier (4) are pressed with almost the same Andruckkräften against the respective opposite inner peripheral portion of the cam carrier (4).
3. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Andruckelemente (26, 31) jedes Nockenträgers (4) mit gleicher Ausrichtung gegen den jeweils gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers (4) angepresst werden.3. Valve drive according to one of the preceding claims, characterized in that the two pressure elements (26, 31) of each cam carrier (4) are pressed with the same orientation against the respective opposite inner peripheral portion of the cam carrier (4).
4. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Andruckelemente (26, 31) beiderseits von einem mit einer Außenverzahnung (15) versehenen Abschnitt der Grundnockenwelle (3) angeordnet sind.4. Valve drive according to one of the preceding claims, characterized in that the two pressure elements (26, 31) on both sides of a with an external toothing (15) provided portion of the base camshaft (3) are arranged.
5. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Andruckelemente (26, 31) jeweils in der Nähe der entgegengesetzten Stirnenden des Nockenträgers (4) angeordnet sind.5. Valve drive according to one of the preceding claims, characterized in that the two pressure elements (26, 31) in each case in the vicinity of the opposite ends of the cam carrier (4) are arranged.
6. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass das Andruckelement (26) der Arretiervorrichtung (24) gegen eine schräge Flanke (28) einer Rastvertiefung (29) angepresst wird, während das weitere Andruckelement (1) gegen eine zylindrische innere Umfangsfläche (33) des Nockenträgers (4) angepresst wird. 6. Valve drive according to one of the preceding claims, characterized in that the pressure element (26) of the locking device (24) against an inclined edge (28) of a latching recess (29) is pressed while the other pressure element (1) against a cylindrical inner peripheral surface (33) of the cam carrier (4) is pressed.
7. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die beiden Andruckelemente (26, 31) jedes Nockenträgers (4) radial einwärts von Nocken (7, 8) auf dem Nockenträger (4) gegen einen gegenüberliegenden inneren Umfangsabschnitt (33) des Nockenträgers (4) angepresst werden.7. Valve drive according to one of the preceding claims, characterized in that the two pressure elements (26, 31) of each cam carrier (4) radially inwardly of cams (7, 8) on the cam carrier (4) against an opposite inner peripheral portion (33) of the Cam carrier (4) are pressed.
8. Ventiltrieb nach Anspruch 7, dadurch gekennzeichnet, dass die beiden Andruckelemente (26, 31) jedes Nockenträgers (4) radial einwärts von einem Punkt zwischen Nockenspitzen zweier benachbarter Nocken (7, 8) gegen einen gegenüberliegenden inneren Umfangsabschnitt (33) des Nockenträgers (4) angepresst werden.8. Valve drive according to claim 7, characterized in that the two pressure elements (26, 31) of each cam carrier (4) radially inwardly from a point between cam tips of two adjacent cams (7, 8) against an opposite inner peripheral portion (33) of the cam carrier ( 4) are pressed.
9. Ventiltrieb nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Andruckelemente (26, 31) verschiedener Nockenträger (4) in Umfangsrich- tung der Grundnockenwelle verdreht sind.9. Valve drive according to one of the preceding claims, characterized in that the pressure elements (26, 31) of different cam carrier (4) are rotated in the circumferential direction of the base camshaft.
10. Ventiltrieb nach Anspruch 9, dadurch gekennzeichnet, dass die Andruckelemente (26, 31) verschiedener Nockenträger (4) dieselbe Winkelausrichtung in Bezug zu Nocken (7, 8) auf den Nockenträgern (4) besitzen.10. Valve gear according to claim 9, characterized in that the pressure elements (26, 31) of different cam carrier (4) have the same angular orientation with respect to cam (7, 8) on the cam carriers (4).
11. Ventiltrieb nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass bei einer Anzahl von n Nockenträgern (4) auf der Grundnockenwelle (3) die Andruckelemente (26, 31) der einzelnen Nockenträger (4) in Umfangsrichtung der Grundnockenwelle (3) um 3607n verdreht sind.11. Valve drive according to claim 9 or 10, characterized in that in a number of n cam carriers (4) on the base camshaft (3) the pressure elements (26, 31) of the individual cam carrier (4) in the circumferential direction of the base camshaft (3) to 3607n are twisted.
12. Ventiltrieb für Gaswechselventile einer Brennkraftmaschine, mit einer Grundnockenwelle, mehreren drehfest und axial verschiebbar auf der Grundnockenwelle geführten Nockenträgem, sowie Arretiervorrichtungen zum Festhalten der Nockenträger in definierten Verschiebestellungen entlang der Grundnockenwelle, wobei die Arretiervorrichtungen jeweils ein Andruckelement umfassen, das in eine Ausnehmung der Grundnockenwelle eingesetzt ist und in radialer Richtung der Grund.nockenwelle gegen einen gegenüberliegenden inneren Umfangsabschnitt des Nockenträgers angepresst wird, dadurch gekennzeichnet, dass die Andruckelemente (26, 31) verschiedener Nockenträger (4) in Umfangsrichtung der Grundnockenwelle (3) gegeneinander verdreht sind.12. Valve gear for gas exchange valves of an internal combustion engine, with a basic camshaft, several rotatably and axially displaceable on the basic cam guided Nockenträgem, and locking devices for holding the cam carrier in defined displacement positions along the basic camshaft, wherein the locking devices each comprise a pressure element in a recess of the basic camshaft is used and is pressed in the radial direction of the Grund.nockenwelle against an opposite inner peripheral portion of the cam carrier, characterized in that the pressure elements (26, 31) of different cam carrier (4) in the circumferential direction of the base camshaft (3) are rotated against each other.
13. Ventiltrieb nach Anspruch 12, dadurch gekennzeichnet, dass die Andruckelemente (26, 31) verschiedener Nockenträger (4) dieselbe Winkelausrichtung in Bezug zu Nocken (7, 8) auf den Nockenträgern (4) besitzen. 13. Valve drive according to claim 12, characterized in that the pressure elements (26, 31) of different cam carrier (4) have the same angular orientation with respect to cam (7, 8) on the cam carriers (4).
14. Ventiltrieb nach Anspruch 12 oder 13, dadurch gekennzeichnet, dass bei einer Anzahl von n Nockenträgern (4) auf der Grundnockenwelle (3) die Andruckelemente (26, 31) der einzelnen Nockenträger (4) in Umfangsrichtung der Grundnockenwelle (3) um 3607n oder um 2 x 3607n verdreht sind. 14. Valve drive according to claim 12 or 13, characterized in that in a number of n cam carriers (4) on the base camshaft (3) the pressure elements (26, 31) of the individual cam carrier (4) in the circumferential direction of the base camshaft (3) to 3607n or twisted by 2 x 3607n.
EP09765507.0A 2008-06-16 2009-05-26 Valve train for gas exchange valves of an internal combustion engine having double-supported cam carriers Active EP2291578B1 (en)

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DE102008028513A DE102008028513A1 (en) 2008-06-16 2008-06-16 Valve operation for gas exchange valves of an internal combustion engine with double-supported cam carriers
PCT/EP2009/003708 WO2009152927A1 (en) 2008-06-16 2009-05-26 Valve train for gas exchange valves of an internal combustion engine having double-supported cam carriers

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Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009055868A1 (en) * 2009-11-26 2011-06-01 Neumayer Tekfor Holding Gmbh camshaft
DE102011103544A1 (en) 2011-06-08 2012-12-13 Schaeffler Technologies AG & Co. KG Storage of a camshaft
DE102011104382A1 (en) 2011-06-16 2012-12-20 Daimler Ag Internal combustion engine valve drive device for a motor vehicle
DE102011116653B4 (en) * 2011-10-21 2023-11-09 Mercedes-Benz Group AG Valve drive device
JP2013185470A (en) * 2012-03-06 2013-09-19 Toyota Motor Corp Rocker arm clip and valve train
DE102012209310A1 (en) * 2012-06-01 2013-12-05 Schaeffler Technologies AG & Co. KG Basic wave for a sliding cam valve drive
DE102012209860A1 (en) 2012-06-13 2013-12-19 Schaeffler Technologies AG & Co. KG Sliding cam valve drive, has cam piece comprising spiral groove, carrier extending along base shaft, actuator fixed to cam piece using pin retractable into spiral groove, and latching unit provided outside cam piece
DE102012210922A1 (en) 2012-06-27 2014-01-02 Schaeffler Technologies AG & Co. KG Component of variable shift cam valve train of internal combustion engine, has locking recesses formed in inner jacket of cam portion such that locking recesses are provided with same axial spacing as holes on ball detent mechanism
JP6161703B2 (en) * 2012-09-14 2017-07-12 マーレ インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツングＭＡＨＬＥ Ｉｎｔｅｒｎａｔｉｏｎａｌ ＧｍｂＨ Camshaft assembly and manufacturing method thereof
JP6003695B2 (en) * 2013-02-06 2016-10-05 マツダ株式会社 Engine valve gear
JP6102338B2 (en) * 2013-02-26 2017-03-29 マツダ株式会社 Engine valve gear
JP5947737B2 (en) 2013-03-07 2016-07-06 日立オートモティブシステムズ株式会社 Variable valve system, control device and variable valve device for internal combustion engine
DE102013005803A1 (en) * 2013-04-04 2014-10-09 Daimler Ag Valve train device for an internal combustion engine
DE102013007741A1 (en) * 2013-05-07 2014-11-13 Thyssenkrupp Presta Teccenter Ag camshaft
JP6070585B2 (en) * 2014-01-21 2017-02-01 マツダ株式会社 Engine valve gear
JP6070586B2 (en) * 2014-01-21 2017-02-01 マツダ株式会社 Method for assembling engine valve gear
DE102014008898B3 (en) * 2014-06-14 2015-08-13 Audi Ag Method for operating an internal combustion engine and corresponding internal combustion engine
DE102014116195A1 (en) * 2014-11-06 2016-05-12 Thyssenkrupp Presta Teccenter Ag Camshaft with at least one axially fixed sliding element
DE102014116252A1 (en) 2014-11-07 2016-05-12 Thyssenkrupp Presta Teccenter Ag Camshaft with an axially guided sliding element
WO2017079383A1 (en) 2015-11-06 2017-05-11 Borgwarner Inc. Valve operating system providing variable valve lift and/or variable valve timing
DE102015224905A1 (en) 2015-12-10 2017-06-14 Thyssenkrupp Ag Method for permanent attachment of cams on a carrier tube
JP6444566B2 (en) * 2016-04-11 2018-12-26 三菱電機株式会社 Solenoid actuator
DE102016222046A1 (en) * 2016-11-10 2018-05-17 Eto Magnetic Gmbh Valve train for an internal combustion engine
DE102016222713B4 (en) * 2016-11-18 2022-02-24 Schaeffler Technologies AG & Co. KG Camshaft with cam piece with reduced number of teeth
CN106593569B (en) * 2016-12-12 2019-02-15 孙德军 A kind of Mechanical course valve actuating gear and control method
JP2018105175A (en) 2016-12-26 2018-07-05 トヨタ自動車株式会社 Variable valve mechanism for engine
DE102017219287A1 (en) 2017-10-26 2019-05-02 Volkswagen Aktiengesellschaft Valve drive for a valve of an internal combustion engine with a locking device and a bracing device
DE102019203432A1 (en) * 2019-03-13 2020-09-17 Mahle International Gmbh Valve train of an internal combustion engine
CN110043340B (en) * 2019-05-15 2020-12-01 杰锋汽车动力系统股份有限公司 VVL camshaft locking structure for internal combustion engine
CN111396166A (en) * 2020-04-16 2020-07-10 昆明云内动力股份有限公司 Cam displacement type variable valve lift system and method
DE102020214554A1 (en) 2020-11-18 2022-05-19 Thyssenkrupp Ag sliding cam arrangement

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0627491B2 (en) * 1985-12-24 1994-04-13 マツダ株式会社 Engine valve drive
JPS6341610A (en) * 1986-08-08 1988-02-22 Mazda Motor Corp Valve driver for engine
KR950005088B1 (en) * 1990-07-10 1995-05-18 미쯔비시 지도샤 고교 가부시끼가이샤 Valve system for automobile engine
JPH0627491A (en) * 1992-07-13 1994-02-04 Nec Corp Production of thin-film transistor
JPH06307216A (en) * 1993-04-20 1994-11-01 Toyota Motor Corp High and low speed switching mechanism in valve system of internal combustion engine
DE4419637A1 (en) 1993-06-17 1994-12-22 Volkswagen Ag Control device for engine valves with at least one deactivatable cam on a cam shaft
US5813377A (en) * 1995-11-07 1998-09-29 Yamaha Hatsudoki Kabushiki Kaisha Engine valve operating system
DE19622174A1 (en) * 1995-12-13 1997-06-26 Porsche Ag Valve train of an internal combustion engine
US5855190A (en) * 1996-09-24 1999-01-05 Yamaha Hatsudoki Kabushiki Kaisha Valve-actuating variable cam for engine
JP2000073731A (en) * 1998-09-03 2000-03-07 Toyota Motor Corp Camshaft bearing structure of internal combustion engine
JP4248131B2 (en) * 2000-07-05 2009-04-02 ヤマハ発動機株式会社 Four-cycle engine valve gear
DE10148179B4 (en) * 2001-09-28 2015-09-24 Schaeffler Technologies AG & Co. KG Valve train with valve lift switching for the gas exchange valves of a 4-stroke internal combustion engine
DE10148243A1 (en) 2001-09-28 2003-04-10 Ina Schaeffler Kg Valve drive with valve lift changing for the gas shuttle valve of a four-stroke internal combustion engine comprises a toothed shaft with an external tooth arrangement
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
DE502004008185D1 (en) * 2003-07-19 2008-11-20 Porsche Ag Valve train for an internal combustion engine
DE102004056290B4 (en) 2004-11-22 2017-03-16 Audi Ag Valve gear of an internal combustion engine with at least one base camshaft
DE102006012386B3 (en) * 2006-03-15 2007-08-30 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Valve gear for internal combustion engine, has cam connected with cam shaft in torque-proof manner, and another cam supported on cam shaft, where latter cam is connectable and separable with former cam by controllable main locking piston
DE102009059712A1 (en) * 2009-12-18 2011-09-22 Thyssenkrupp Presta Teccenter Ag Cam unit for a built camshaft
KR101438622B1 (en) * 2012-12-28 2014-09-15 현대자동차 주식회사 Variable valve lift device
JP6102651B2 (en) * 2013-09-18 2017-03-29 マツダ株式会社 Engine valve gear

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009152927A1 *

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WO2009152927A9 (en) 2011-03-31
CN102132014B (en) 2015-03-04
JP5367073B2 (en) 2013-12-11
US20110180027A1 (en) 2011-07-28
WO2009152927A1 (en) 2009-12-23
CN102132014A (en) 2011-07-20
EP2291578B1 (en) 2015-11-25
US9103243B2 (en) 2015-08-11
JP2011524482A (en) 2011-09-01
DE102008028513A1 (en) 2009-12-24

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