EP1427918B1 - Valve mechanism for an internal combustion engine - Google Patents

Valve mechanism for an internal combustion engine Download PDF

Info

Publication number
EP1427918B1
EP1427918B1 EP02769980A EP02769980A EP1427918B1 EP 1427918 B1 EP1427918 B1 EP 1427918B1 EP 02769980 A EP02769980 A EP 02769980A EP 02769980 A EP02769980 A EP 02769980A EP 1427918 B1 EP1427918 B1 EP 1427918B1
Authority
EP
European Patent Office
Prior art keywords
inlet
valve
outlet
lift
valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02769980A
Other languages
German (de)
French (fr)
Other versions
EP1427918A1 (en
Inventor
Armin Josenhans
Dietmar Schwarzenthal
Leo Spiegel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE10212327A external-priority patent/DE10212327A1/en
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP1427918A1 publication Critical patent/EP1427918A1/en
Application granted granted Critical
Publication of EP1427918B1 publication Critical patent/EP1427918B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • F01L1/0532—Camshafts overhead type the cams being directly in contact with the driven valve
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • 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
    • F01L13/0005—Deactivating valves
    • 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
    • F01L2307/00—Preventing the rotation of tappets

Definitions

  • the invention relates to a valve drive for an internal combustion engine according to the preamble of claim 1.
  • Variable valve trains are known from the prior art with which both the valve opening times and the valve opening cross section can be adapted to the operating state of the engine.
  • a variable valve train an internal combustion engine known in which by means of a switchable bucket tappet valve lift is two-stage adjustable.
  • the device is supplemented by a device for adjusting the inlet and outlet times of the gas exchange valves, which, inter alia, the cylinder filling can be improved over a wide speed range.
  • the object of the invention is, on the basis of o.
  • a valve train for an internal combustion engine in which one of two identical gas exchange valves via a cam follower is applied, wherein the cam follower is switchable to a large valve lift and a zero stroke.
  • a second gas exchange valve is simultaneously acted upon by a further cam follower, which can also be coupled to a large valve lift, but alternatively to a small valve lift.
  • a changeover can take place such that only one of the cam followers is switched and the other cam follower remains in a previously set coupling position.
  • An advantageous structural implementation is characterized in that at least part of the hydraulic supply lines for the valve lift switching are formed as channels in a tappet housing.
  • a valve train according to the DE 196 30 192 A1 be retrofitted in a simple manner only by replacing the tappet housing with the inventive technique.
  • the device for changing the valve opening times is supplemented by a arranged on the inlet and / or outlet camshaft adjuster, with the help of the inlet and / or outlet of the gas exchange valves can be changed.
  • two gas exchange valves 2 shown represent part of a valve train of a four-valve engine, in which the two gas exchange valves 2 exemplarily form the two intake valves of a cylinder; the two provided per cylinder Exhaust valves are not shown; However, they are designed in terms of their construction and their operation analogous to the inlet side described in more detail below.
  • the two gas exchange valves 2 are actuated via a designed as a bucket tappet Hubübertragungselement 4 of the cams 6, 7 of a camshaft 8.
  • the tappets 4 are inserted into a bore 9 of a cylinder head 11 and are supported by a compression spring 10.
  • the gas exchange valves 2 comprise a valve disk 14, which cooperates with a valve seat 12 of the cylinder head 11, and a valve stem 16, which is provided with a valve spring plate 18. Between valve spring plate 18 and cylinder head 11, a valve spring 20 is arranged, which holds the gas exchange valve 2 in the closed position.
  • the compression spring 10 is supported on the opposite side also on the valve spring plate 18.
  • the tappet 4 has two cup members arranged concentrically with each other, hereinafter referred to as the outer reciprocating piston 22 and the inner reciprocating piston 23, which cooperate with different cam regions (partial cams) 24 to 26 or 24 'to 26' of the cams 6 and 7.
  • the two outer cam portions 24, 26 and 24 ', 26' of the cams 6 and 7 are formed equal to each other, d. H. They have the same lifting height and phase angle. These cam portions 24 and 26 or 24 'and 26' cooperate with the outer piston 22.
  • the central cam area 25 or 25 ' has a lower lifting height compared to the two outer cam areas 24 and 26 or 24' and 26 'and interacts with the inner lifting piston 23.
  • the outer cam portion 24, 26 of the cam 6 in turn has a greater lifting height than the outer cam portion 24 ', 26' of the cam 7; the lifting height of the central cam portion 25 of the cam 6, however, is smaller than the lifting height of the central cam portion 25 'of the cam 7.
  • the two reciprocating pistons 22 and 23 have in the bottom area a bore 27 which in the base circle phase of the three partial cams 24 and 24 ', 25 and 25' and 26 and 26 '(see Fig. 3 ) are aligned with each other, so that the outer with the inner reciprocating piston 22, 23 in this position by in the bore 27 longitudinally displaceable piston elements 28, 29th is lockable.
  • the displacement of the piston elements 28, 29 and thus the locking takes place hydraulically;
  • an end face of the piston 28 is acted upon by hydraulic oil via an opening 33.
  • On the locking mechanism will not be discussed in detail; this is for example in the DE 196 01 587 A1 or the DE 195 28 505 A1 described in more detail.
  • the circuit diagram for the hydraulic pressure oil supply for valve lift switching is shown on the basis of a row of cylinders of a two-row six-cylinder gasoline engine with four-valve technology (see Fig. 1 ).
  • the bucket tappets 4 of the first three inlet valves EV1 are connected to a first hydraulic line 34 which leads via a first switching valve (2/2-way valve) 36 to an oil sump 38 of the engine.
  • the tappets 4 associated with the second three inlet valves EV2 are connected to a second hydraulic line 40, which likewise leads to the oil sump 38 via a second switching valve (2/2-way valve).
  • the bucket tappets are 4 of the first three Exhaust valves AV1 of the three cylinders 30 to 32 connected to a third hydraulic line 44, which also leads via a third switching valve (2/2-way valve) 46 to the oil sump 38.
  • a fourth hydraulic line 48 is connected to the bucket tappets 4 which are associated with the three second exhaust valves AV2 and which leads via a fourth switching valve (2/2 way valve) 50 to the oil sump 38.
  • the four switching valves 36, 42, 46 and 50 are connected to a pressure oil supply line 52, which can be acted upon by an oil feed pump 54 with hydraulic oil.
  • the outer partial cams 24 and 26 differ from the outer partial cams 24 'and 26' as well as the central partial cams 25 and 25 'with regard to their stroke and their phase position. This results in the in Fig. 5 illustrated valve lift curves with a small valve lift h EV1 and a large valve lift H EV1 for the first intake valves EV1 and with a small valve lift h EV2 and a large valve lift H EV2 for the second intake valves EV2.
  • valve lift can be used in any other engine configurations in which each cylinder at least two inlet or outlet valves are provided.
  • camshaft adjusters 56 and 58 are provided on the intake and exhaust side, by means of which the valve timing on the intake and exhaust side of the internal combustion engine can be adjusted to "early” or “late” depending on the operating condition.
  • the two camshaft adjusters 56 and 58 are connected via a 3/2-way valve designed switching valve 60 and 62, each with a first control line 64, 65 to the pressure oil - supply line 52, while in each case a second control line 66, 67 to the oil sump 38 of the internal combustion engine returns.
  • the structure of such camshaft adjuster 56, 58 is for example in the DE 198 34 843 A1 described and illustrated.
  • a bucket tappet housing 68 has openings 70, in which the individual switchable tappets 4 record.
  • two longitudinal bores 72 and 74 are provided, in which two mold inserts 76 and 78 are used to form two partial oil channels 72a, 72b and 74a, 74b.
  • two longitudinal grooves 80a, b and 82a, b are introduced to form the partial oil channels 72a, b and 74a, b.
  • the mold inserts 76, 78 also have circumferentially distributed groove-shaped radial recesses 84a to 84f and 86a to 86f connected to the longitudinal grooves 80a, b and 82a, b, respectively.
  • the recesses 84, 86 are each provided with in the housing 68 oil passages 88, 90 connected to the switching of the tappets 4 to the in FIG. 3 lead shown openings 33.
  • To seal the-Formeinlegemaschine 76, 78 whose end faces are glued into the holes 72, 74 or there are separate Abdichtstutzen (not shown) pressed at the two ends of the holes.
  • the mold inserts 76, 78 are preferably made the same material as the tappet housing 68, ie aluminum; however, other materials such as plastic are equally applicable.
  • openings 94a to 94d are still visible, which serve to accommodate the four switching valves 36, 42, 46, 50, which are not shown for clarity in the tappet housing 68 itself.
  • the openings 94a to 94d are in each case in communication with one of the partial oil channels 72a, b and 74a, b, in this case opening 94a with oil channel 72b, opening 94b with oil channel 74a, opening 94c with oil channel 72a and opening 94d with oil channel 74b.
  • identifiable external pressure lines 96a and 96b serve that the oil pressure applied to both openings 94c and 94d for switching the valves 36, 42 is also supplied in parallel to the openings 94a and 94b for switching the valves 46, 50.

Landscapes

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

Abstract

The invention relates to a valve mechanism for an internal combustion engine, comprising at least two inlet and/or outlet valves (EV1, EV2, AV1, AV2) per cylinder which can be activated by the inlet and/or outlet camshaft (8); in addition to lift transmission elements (4) which are arranged between the camshafts (6,7) of the inlet and/or outlet camshaft, and means for altering the valve lift of the inlet and/or outlet valves. At least two inlet valves and/or two outlet valves per cylinder cooperate with at least two partial cams (24, 25, 26) having two different lift curves, and the lift transmission elements (4) of the gas exchange valves are provided with at least two lift elements (22, 23) which respectively cooperate with the partial cams (24, 25, 26) and with the hydraulic supply lines for switching purposes. According to the invention, the supply lines (34, 44) for switching a first inlet or outlet valve (EV1, AV2) are separate from the supply lines (40, 48) for switching a second inlet or outlet valve (EV2, AV2), whereby a first inlet or outlet valve (EV1, AV1) can be switched independently from the second inlet or outlet valve (EV2, AV2). As a result two-step valve switching can be achieved in a simple manner.

Description

Die Erfindung betrifft einen Ventiltrieb für eine Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a valve drive for an internal combustion engine according to the preamble of claim 1.

Aus dem Stand der Technik sind variable Ventiltriebe bekannt, mit denen sowohl die Ventilöffnungszeiten als auch der Ventilöffnungsquerschnitt dem Betriebszustand des Motors angepasst werden kann. So ist beispielsweise aus der DE 196 06 054 C2 ein variabler Ventiltrieb einer Brennkraftmaschine bekannt, bei dem mit Hilfe eines schaltbaren Tassenstößels der Ventilhub zweistufig einstellbar ist. Ergänzt wird die Vorrichtung durch eine Einrichtung zum Verstellen der Ein- und Auslasszeiten der Gaswechselventile, wodurch u. a. die Zylinderfüllung über einen großen Drehzahlbereich verbessert werden kann.Variable valve trains are known from the prior art with which both the valve opening times and the valve opening cross section can be adapted to the operating state of the engine. For example, from the DE 196 06 054 C2 a variable valve train an internal combustion engine known in which by means of a switchable bucket tappet valve lift is two-stage adjustable. The device is supplemented by a device for adjusting the inlet and outlet times of the gas exchange valves, which, inter alia, the cylinder filling can be improved over a wide speed range.

Aufgabe der Erfindung ist es, auf der Grundlage des o. a. Standes der Technik die Zweistufigkeit des Ventilhubs eines gattungsgemäßen Ventiltriebs auszubauen, um angepasst an den Last- und Drehzahlzustand des Motors, den Wirkungsgrad der Brennkraftmaschine weiter zu steigern.The object of the invention is, on the basis of o. A. Prior art to expand the two-stage valve lift of a generic valve train to adapt to the load and speed condition of the engine to further increase the efficiency of the internal combustion engine.

Aus der EP 0 259 106 A1 ist ein Ventiltrieb mit einer Kipphebelanordnung bekannt (sog. Honda- VTEC- System), bei dem durch drei verschiedene Nocken unterschiedliche Ventilhubkombinationen umsetzbar sind. Dazu wird ein nicht unmittelbar auf die Ventile wirkender Kipphebel, der zwischen den beiden unmittelbar auf die Einlassventile wirkenden Kipphebeln angeordnet ist, über hydraulisch ansteuerbare Verriegelungselemente wahlweise mit den beiden Kipphebeln verbunden. Zur Ansteuerung der Verriegelungselemente ist weiterhin in einem Ölkanal der Kipphebelwelle ein Einlegeteil vorgesehen, durch das mehrere separate Teilölkanäle ausgebildet werden.From the EP 0 259 106 A1 is a valve train with a rocker arm assembly known (so-called Honda VTEC system), in which different valve lift combinations can be implemented by three different cams. For this purpose, a rocker arm, which does not act directly on the valves and is arranged between the two rocker arms acting directly on the intake valves, is selectively connected to the two rocker arms via hydraulically controllable locking elements. For driving the locking elements, an insert part is further provided in an oil passage of the rocker shaft through which a plurality of separate partial oil channels are formed.

Aus der DE 196 02 013 A1 ist ein Ventiltrieb für eine Brennkraftmaschine bekannt, bei dem ein von zwei gleichwirkenden Gaswechselventilen über einen Nockenfolger beaufschlagt wird, wobei der Nockenfolger auf einen großen Ventilhub und einen Null-Hub umschaltbar ist. Dabei ist ein zweites Gaswechselventil gleichzeitig von einem weiteren Nockenfolger beaufschlagt, der ebenfalls auf einen großen Ventilhub, jedoch alternativ auf einen kleinen Ventilhub koppelbar ist. Weiterhin kann eine Umschaltung derart erfolgen, dass lediglich einer der Nockenfolger geschaltet wird und der andere Nockenfolger in einer bis dahin eingestellten Koppelposition verbleibt.From the DE 196 02 013 A1 a valve train for an internal combustion engine is known, in which one of two identical gas exchange valves via a cam follower is applied, wherein the cam follower is switchable to a large valve lift and a zero stroke. In this case, a second gas exchange valve is simultaneously acted upon by a further cam follower, which can also be coupled to a large valve lift, but alternatively to a small valve lift. Furthermore, a changeover can take place such that only one of the cam followers is switched and the other cam follower remains in a previously set coupling position.

Die eingangs gestellte Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst. Dadurch, dass die Hubübertragungselemente für die Gaswechselventile hydraulisch separat ansteuerbar sind, kann die Variabilität für den Ventilöffnungsquerschnitt bzw. für die Ventilöffnungszeiten der Zylinder in Abhängigkeit vom Last bzw. Drehzahlzustand erhöht werden. So ist es beispielsweise möglich, auf der Einlassseite für das erste Einlassventil einen kleinen Ventilhub zu verwenden, während für ein zweites Einlassventil des betreffenden Zylinders der große Ventilhub realisiert ist.The object stated in the introduction is achieved by the features of claim 1. Due to the fact that the Hubübertragungselemente for the Gas exchange valves are hydraulically controlled separately, the variability for the valve opening cross section and for the valve opening times of the cylinder can be increased depending on the load or speed state. For example, it is possible to use a small valve lift on the intake side for the first intake valve, while the large valve lift is realized for a second intake valve of the relevant cylinder.

Durch die in den Unteransprüchen angegebenen Merkmale sind vorteilhafte Weiterbildungen der Erfindung möglich.The features specified in the dependent claims advantageous developments of the invention are possible.

Durch die separate hydraulische Ansteuerung für die Ventilhubumschaltung innerhalb eines Zylinders besteht die Möglichkeit, die Hubkurven des kleinen und/oder des großen Nockens des ersten Ein- oder Auslassventils gegenüber den Hubkurven des zweiten Ein- oder Auslassventils des betreffenden Zylinders unterschiedlich zu gestalten. Damit wird die Variabilität der möglichen Ventilhubeinstellungen weiter erhöht.Due to the separate hydraulic control for the valve lift switching within a cylinder, it is possible to make the lift curves of the small and / or large cam of the first inlet or outlet valve with respect to the lift curves of the second inlet or outlet valve of the respective cylinder differently. This further increases the variability of the possible valve lift settings.

Eine vorteilhafte konstruktive Umsetzung zeichnet sich dadurch aus, dass mindestens ein Teil der hydraulischen Versorgungsleitungen für die Ventilhubumschaltung als Kanäle in einem Tassenstösselgehäuse ausgebildet sind. Damit kann z.B. ein Ventiltrieb gemäß der DE 196 30 192 A1 auf einfache Art und Weise lediglich durch Austausch des Tassenstösselgehäuses mit der erfindungsgemäßen Technik nachgerüstet werden.An advantageous structural implementation is characterized in that at least part of the hydraulic supply lines for the valve lift switching are formed as channels in a tappet housing. Thus, for example, a valve train according to the DE 196 30 192 A1 be retrofitted in a simple manner only by replacing the tappet housing with the inventive technique.

Für die Ausbildung der für die Druckölversorgung der einzelnen Tassenstössel erforderlichen Ölkanäle wird vorgeschlagen, Formeinlegeteile zu verwenden, die in entsprechenden Bohrungen des Tassenstösselgehäuses Aufnahme finden. Die in ihrer Grundform zylinderförmigen Formeinlegeteile sind mit zwei Längsnuten sowie mit radialen Aussparungen versehen, wobei letztere mit zu den Tassenstösseln führenden Ölbohrungen verbunden sind. Damit wird insgesamt eine platzsparende und wenig zusätzliche Bauteile benötigende Öldruckversorgung für den variablen Ventiltrieb im Zylinderkopf der Brennkraftmaschine zur Verfügung gestellt.For the formation of the required for the pressure oil supply of the individual tappets oil channels is proposed to use Formeinlegeteile, which find in corresponding holes in the tappet housing. The cylindrical shape inserts in their basic form are provided with two longitudinal grooves and with radial recesses, the latter being connected to oil bores leading to the cup tappets. For a total of space-saving and little additional components requiring oil pressure supply for the variable valve train in the cylinder head of the engine is provided.

Für die Ansteuerung der Ölkanäle sind im Tassenstösselgehäuse entsprechende Aufnahmen für die Schaltventile vorgesehen.For the control of the oil channels corresponding receptacles for the switching valves are provided in the bucket tappet housing.

Die Vorrichtung zur Änderung der Ventilöffnungszeiten wird ergänzt durch einen auf der Ein- und/oder Auslassseite angeordneten Nockenwellenversteller, mit dessen Hilfe die Ein- und/oder Auslasszeiten der Gaswechselventile verändert werden können.The device for changing the valve opening times is supplemented by a arranged on the inlet and / or outlet camshaft adjuster, with the help of the inlet and / or outlet of the gas exchange valves can be changed.

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert.An embodiment of the invention is explained in more detail in the following description and drawings.

Es zeigen

Fig. 1
ein Schaltschema für einen variablen Ventiltrieb,
Fig. 2
die schematische Darstellung eines-Ventiltriebs,
Fig. 3
einen Querschnitt durch ein Hubübertragungselement,
Fig. 4
einen Längsschnitt durch ein Hubübertragungselement,
Fig. 5
ein Diagramm zur Darstellung verschiedener Ventilerhebungskurven,
Fig. 6
eine tabellarische Übersicht über verschiedene Schaltzustände des Ventiltriebs,
Fig. 7
eine Draufsicht auf ein Tassenstösselgehäuse,
Fig. 8
einen Schnitt entlang der Linie VIII-VIII gemäß Fig. 7,
Fig. 9
einen Schnitt entlang der Linie IX-IX gemäß Fig. 7,
Fig. 10
einen Schnitt entlang der Linie X-X gemäß Fig. 7,
Fig. 11
einen Schnitt entlang der Linie XI-XI gemäß Fig. 7 und
Fig. 12
in Bohrungen des Tassenstösselgehäuses eingesetzte Einlegeteile,
Fig. 13
einen Schnitt entlang der Linie Xlll-XIII gemäß Fig. 12 und
Fig. 14
einen Schnitt entlang der Linie XIV-XIV gemäß Fig. 12.
Show it
Fig. 1
a circuit diagram for a variable valve train,
Fig. 2
the schematic representation of a valve train,
Fig. 3
a cross section through a Hubübertragungselement,
Fig. 4
a longitudinal section through a Hubübertragungselement,
Fig. 5
a diagram illustrating various valve lift curves,
Fig. 6
a tabular overview of various switching states of the valve train,
Fig. 7
a top view of a bucket tappet housing,
Fig. 8
a section along the line VIII-VIII according to Fig. 7 .
Fig. 9
a section along the line IX-IX according to Fig. 7 .
Fig. 10
a section along the line XX according to Fig. 7 .
Fig. 11
a section along the line XI-XI according to Fig. 7 and
Fig. 12
inserts inserted in bores of the tappet housing,
Fig. 13
a section along the line XIII-XIII according to Fig. 12 and
Fig. 14
a section along the line XIV-XIV according to Fig. 12 ,

Die in Fig. 2 dargestellten zwei Gaswechselventile 2 stellen einen Teil eines Ventiltriebs eines Vierventil- Motors dar, bei dem die beiden Gaswechselventile 2 exemplarisch die beiden Einlassventile eines Zylinders bilden; die zwei pro Zylinder vorgesehenen Auslaßventile sind nicht dargestellt; sie sind jedoch hinsichtlich ihres Aufbaus und ihrer Betätigung analog zu der im folgenden näher beschriebenen Einlassseite ausgeführt. Die beiden Gaswechselventile 2 werden über ein als Tassenstößel ausgebildetes Hubübertragungselement 4 von den Nocken 6, 7 einer Nockenwelle 8 betätigt. Die Tassenstößel 4 sind in einer Bohrung 9 eines Zylinderkopfes 11 eingesetzt und stützen sich über eine Druckfeder 10 ab. Die Gaswechselventile 2 umfassen einen mit einem Ventilsitz 12 des Zylinderkopfes 11 zusammenwirkenden Ventilteller 14 sowie einen Ventilschaft 16, der mit einem Ventilfederteller 18 versehen ist. Zwischen Ventilfederteller 18 und Zylinderkopf 11 ist eine Ventilfeder 20 angeordnet, die das Gaswechselventil 2 in der geschlossenen Stellung hält. Die Druckfeder 10 stützt sich auf der gegenüberliegenden Seite ebenfalls am Ventilfederteller 18 ab.In the Fig. 2 two gas exchange valves 2 shown represent part of a valve train of a four-valve engine, in which the two gas exchange valves 2 exemplarily form the two intake valves of a cylinder; the two provided per cylinder Exhaust valves are not shown; However, they are designed in terms of their construction and their operation analogous to the inlet side described in more detail below. The two gas exchange valves 2 are actuated via a designed as a bucket tappet Hubübertragungselement 4 of the cams 6, 7 of a camshaft 8. The tappets 4 are inserted into a bore 9 of a cylinder head 11 and are supported by a compression spring 10. The gas exchange valves 2 comprise a valve disk 14, which cooperates with a valve seat 12 of the cylinder head 11, and a valve stem 16, which is provided with a valve spring plate 18. Between valve spring plate 18 and cylinder head 11, a valve spring 20 is arranged, which holds the gas exchange valve 2 in the closed position. The compression spring 10 is supported on the opposite side also on the valve spring plate 18.

Der Tassenstößel 4 weist zwei konzentrisch zueinander angeordnete Tassenelemente auf, im folgenden als äußerer Hubkolben 22 und innerer Hubkolben 23 bezeichnet, die jeweils mit unterschiedlichen Nockenbereichen (Teilnocken) 24 bis 26 bzw. 24' bis 26' der Nocken 6 und 7 zusammenwirken. Die beiden äußeren Nockenbereiche 24, 26 und 24', 26' der Nocken 6 und 7 sind untereinander gleich ausgebildet, d. h. sie haben die gleiche Hubhöhe und Phasenlage. Diese Nockenbereiche 24 und 26 bzw. 24' und 26' wirken mit dem äußeren Hubkolben 22 zusammen. Der mittlere Nockenbereich 25 bzw. 25' hat gegenüber den beiden äußeren Nockenbereichen 24 und 26 bzw. 24' und 26' eine geringere Hubhöhe und wirkt mit dem inneren Hubkolben 23 zusammen. Der äußere Nockenbereich 24, 26 des Nockens 6 weist wiederum eine größere Hubhöhe auf als der äußere Nockenbereich 24', 26' des Nockens 7; die Hubhöhe des mittleren Nockenbereichs 25 des Nockens 6 ist dagegen kleiner als die Hubhöhe des mittleren Nockenbereichs 25'des Nockens 7.The tappet 4 has two cup members arranged concentrically with each other, hereinafter referred to as the outer reciprocating piston 22 and the inner reciprocating piston 23, which cooperate with different cam regions (partial cams) 24 to 26 or 24 'to 26' of the cams 6 and 7. The two outer cam portions 24, 26 and 24 ', 26' of the cams 6 and 7 are formed equal to each other, d. H. They have the same lifting height and phase angle. These cam portions 24 and 26 or 24 'and 26' cooperate with the outer piston 22. The central cam area 25 or 25 'has a lower lifting height compared to the two outer cam areas 24 and 26 or 24' and 26 'and interacts with the inner lifting piston 23. The outer cam portion 24, 26 of the cam 6 in turn has a greater lifting height than the outer cam portion 24 ', 26' of the cam 7; the lifting height of the central cam portion 25 of the cam 6, however, is smaller than the lifting height of the central cam portion 25 'of the cam 7.

Die beiden Hubkolben 22 und 23 weisen im Bodenbereich eine Bohrung 27 auf, die in der Grundkreisphase der drei Teilnocken 24 bzw. 24', 25 bzw. 25' sowie 26 bzw. 26' (siehe Fig. 3) zueinander fluchten, so dass der äußere mit dem inneren Hubkolben 22, 23 in dieser Stellung durch in der Bohrung 27 längsverschiebbare Kolbenelemente 28, 29 verriegelbar ist. Die Verschiebung der Kolbenelemente 28, 29 und damit die Verriegelung erfolgt hydraulisch; zu diesem Zweck wird über eine Öffnung 33 eine Stirnfläche des Kolbens 28 mit Hydrauliköl beaufschlagt. Auf den Verriegelungsmechanismus wird nicht näher eingegangen; dieser ist beispielsweise in der DE 196 01 587 A1 oder der DE 195 28 505 A1 näher beschrieben. Sind in einer ersten Arbeits- bzw. Schaltstellung der äußere und innere Hubkolben 22 und 23 über die Kolbenelemente 28, 29 zueinander verriegelt, so wird über die äußeren Nockenbereiche 24 und 26 bzw. 24' und 26' der größere Ventilhub auf den Ventilschaft 16 des Gaswechselventils 2 übertragen. Wird über ein entsprechendes Umschalten der in hydraulischen Zuleitungen angeordneten Steuerventile (später noch näher erläutert) der auf den Kolben 28 ausgeübte Druck soweit reduziert, dass die Kolben 28, 29 aus ihrer verriegelten Arbeitsstellung zurückgeführt werden, sind die beiden Hubkolben 22 und 23 wieder frei beweglich zueinander, so dass lediglich die durch den mittleren Teilnocken 25 bzw. 25' verursachte Hubbewegung über den inneren Hubkolben 23 auf den Ventilschaft 16 des Gaswechselventils 2 übertragen wird. Der äußeren Hubkolben 22 folgt dem Hubverlauf der beiden äußeren Teilnocken 24 bzw. 24' und 26 bzw. 26', ohne jedoch Einfluss auf den frei dazu beweglichen inneren Hubkolben 23 zu haben.The two reciprocating pistons 22 and 23 have in the bottom area a bore 27 which in the base circle phase of the three partial cams 24 and 24 ', 25 and 25' and 26 and 26 '(see Fig. 3 ) are aligned with each other, so that the outer with the inner reciprocating piston 22, 23 in this position by in the bore 27 longitudinally displaceable piston elements 28, 29th is lockable. The displacement of the piston elements 28, 29 and thus the locking takes place hydraulically; For this purpose, an end face of the piston 28 is acted upon by hydraulic oil via an opening 33. On the locking mechanism will not be discussed in detail; this is for example in the DE 196 01 587 A1 or the DE 195 28 505 A1 described in more detail. Are in a first working or switching position of the outer and inner reciprocating piston 22 and 23 via the piston elements 28, 29 locked to each other, so is on the outer cam portions 24 and 26 or 24 'and 26' of the larger valve lift on the valve stem 16 of the Gas exchange valve 2 transferred. If the pressure exerted on the piston 28 is reduced to such an extent that the pistons 28, 29 are returned from their locked working position via a corresponding changeover of the control valves arranged in hydraulic feed lines (to be explained later), the two reciprocating pistons 22 and 23 are again freely movable to one another, so that only the lifting movement caused by the central part cam 25 or 25 'is transmitted via the inner lifting piston 23 to the valve stem 16 of the gas exchange valve 2. The outer lifting piston 22 follows the stroke course of the two outer part cam 24 or 24 'and 26 or 26', but without having any influence on the freely movable inner reciprocating piston 23.

Das Schaltschema für die hydraulische Druckölversorgung zur Ventilhubumschaltung ist anhand einer Zylinderbankreihe eines zweireihigen 6- Zylinder- Ottomotors mit Vierventiltechnik dargestellt (siehe Fig. 1). Dazu werden die Tassenstößel 4 der beiden Einlassventile EV1 und EV2 sowie die Tassenstößel 4 der beiden Auslassventile AV1 und AV2 der drei dargestellten Zylinder 30, 31 und 32 zur Ver- bzw. Entriegelung der beiden Hubkolben 22, 23 und damit zur Steuerung des Ventilhubs separat mit Hydrauliköl beaufschlagt. Weiterhin sind die Tassenstößel 4 der ersten drei Einlassventile EV1 mit einer ersten Hydraulikleitung 34 verbunden, die über ein erstes Schaltventil (2/2-Wegeventil) 36 zu einem Ölsumpf 38 des Motors führt. Die den zweiten drei Einlassventilen EV2 zugeordneten Tassenstößel 4 sind mit einer zweiten Hydraulikleitung 40 verbunden, die über ein zweites Schaltventil (2/2- Wegeventil) 42 ebenfalls zum Ölsumpf 38 führt. Auf analoge Art und Weise sind die Tassenstößel 4 der drei ersten Auslassventile AV1 der drei Zylinder 30 bis 32 mit einer dritten Hydraulikleitung 44 verbunden, die über ein drittes Schaltventil (2/2- Wegeventil) 46 ebenfalls zum Ölsumpf 38 führt. Eine vierte Hydraulikleitung 48 ist mit den Tassenstößeln 4 verbunden, die den drei zweiten Auslassventilen AV2 zugeordnet sind und die über ein viertes Schaltventil (2/2 Wegeventil) 50 zum Ölsumpf 38 führt. Die vier Schaltventile 36, 42, 46 und 50 sind an eine Drucköl - Versorgungsleitung 52 angeschlossen, die über eine Ölförderpumpe 54 mit Hydrauliköl beaufschlagbar ist.The circuit diagram for the hydraulic pressure oil supply for valve lift switching is shown on the basis of a row of cylinders of a two-row six-cylinder gasoline engine with four-valve technology (see Fig. 1 ). For this purpose, the tappets 4 of the two intake valves EV1 and EV2 and the tappets 4 of the two exhaust valves AV1 and AV2 of the three illustrated cylinders 30, 31 and 32 for locking or unlocking the two reciprocating pistons 22, 23 and thus to control the valve lift separately Hydraulic oil applied. Furthermore, the bucket tappets 4 of the first three inlet valves EV1 are connected to a first hydraulic line 34 which leads via a first switching valve (2/2-way valve) 36 to an oil sump 38 of the engine. The tappets 4 associated with the second three inlet valves EV2 are connected to a second hydraulic line 40, which likewise leads to the oil sump 38 via a second switching valve (2/2-way valve). In an analogous way, the bucket tappets are 4 of the first three Exhaust valves AV1 of the three cylinders 30 to 32 connected to a third hydraulic line 44, which also leads via a third switching valve (2/2-way valve) 46 to the oil sump 38. A fourth hydraulic line 48 is connected to the bucket tappets 4 which are associated with the three second exhaust valves AV2 and which leads via a fourth switching valve (2/2 way valve) 50 to the oil sump 38. The four switching valves 36, 42, 46 and 50 are connected to a pressure oil supply line 52, which can be acted upon by an oil feed pump 54 with hydraulic oil.

In Abhängigkeit der Stellung der Schaltventile 36, 42, 46, 50 lassen sich verschiedene Ventilhubkombinationen realisieren. Wie bereits eingangs erläutert, unterscheiden sich die äußeren Teilnocken 24 und 26 von den äußeren Teilnocken 24' und 26' sowie die mittleren Teilnocken 25 und 25' hinsichtlich ihres Hubs und ihrer Phasenlage. Damit ergeben sich die in Fig. 5 dargestellten Ventilerhebungskurven mit einem kleinen Ventilhub hEV1 und einem grossen Ventilhub HEV1 für die ersten Einlassventile EV1 sowie mit einem kleinen Ventilhub hEV2 und einem großen Ventilhub HEV2 für die zweiten Einlassventile EV2. Analog dazu ergeben sich verschiedene Erhebungskurven für die Auslassventile AV1 und AV2: einen kleinen Ventilhub hAV1 und einen grossen Ventilhub HAV1 für die ersten Auslassventile AV1 und einen kleinen Ventilhub hAV2 und einen grossen Ventilhub HAV2 für die zweiten Auslassventile AV2. So lassen sich bezogen auf das in Fig. 1 dargestellte Ausführungsbeispiel 16 verschiedene Schaltvariationen realisieren, mit denen die Brennkraftmaschine in Abhängigkeit vom Last und Drehzahlzustand betrieben werden kann. Die mit Hilfe der Schaltventile 36, 42, 46, 50 umsetzbaren Ventilhubkombinationen sind anhand der in Fig. 6 dargestellten Tabelle aufgezeigt. Selbstverständlich ist es auch denkbar, je nach Verwendungszweck lediglich die Einlass- oder die Auslassseite der Brennkraftmaschine mit den mehrstufigen Ventilhub - Schaltmöglichkeiten zu versehen. Darüber hinaus ist die beschriebene Ventilhubumschaltung bei beliebig anderen Motorkonfigurationen einsetzbar, bei denen je Zylinder mindestens zwei Einlass- oder Auslassventile vorgesehen sind.Depending on the position of the switching valves 36, 42, 46, 50 can be realized different Ventilhubkombinationen. As already explained at the outset, the outer partial cams 24 and 26 differ from the outer partial cams 24 'and 26' as well as the central partial cams 25 and 25 'with regard to their stroke and their phase position. This results in the in Fig. 5 illustrated valve lift curves with a small valve lift h EV1 and a large valve lift H EV1 for the first intake valves EV1 and with a small valve lift h EV2 and a large valve lift H EV2 for the second intake valves EV2. Similarly, there are various elevation curves for the exhaust valves AV1 and AV2: a small valve lift h AV1 and a large valve lift H AV1 for the first exhaust valves AV1 and a small valve lift h AV2 and a large valve lift H AV2 for the second exhaust valves AV2. So can be related to the in Fig. 1 illustrated embodiment 16 realize different switching variations with which the internal combustion engine can be operated in dependence on the load and speed state. The by means of the switching valves 36, 42, 46, 50 implementable Ventilhubkombinationen are based on the in Fig. 6 shown table. Of course, it is also conceivable to provide only the inlet or the exhaust side of the internal combustion engine with the multi-stage valve lift - switching options depending on the intended use. In addition, the described valve lift can be used in any other engine configurations in which each cylinder at least two inlet or outlet valves are provided.

Die Möglichkeiten zur Einstellung der Ventilhübe der Brennkraftmaschine kann durch eine zusätzliche Einrichtung zur Änderung der Einlass- und/oder Auslasszeiten der Gaswechselventile 2 sinnvoll ergänzt werden. Dazu sind auf der Einlass- und der Auslassseite zwei Nockenwellenversteller 56 und 58 vorgesehen, mit deren Hilfe die Ventilsteuerzeiten auf der Einlass- und der Auslassseite der Brennkraftmaschine in Abhängigkeit vom Betriebszustand nach "früh" oder "spät" verstellt werden können. Dazu sind die beiden Nockenwellenversteller 56 und 58 über ein als 3/2- Wegeventil ausgebildetes Schaltventil 60 und 62 mit jeweils einer ersten Steuerleitung 64, 65 an die Drucköl - Versorgungsleitung 52 angeschlossen, während jeweils eine zweite Steuerleitung 66, 67 zum Ölsumpf 38 der Brennkraftmaschine zurückführt. Der Aufbau derartiger Nockenwellenversteller 56, 58 ist beispielsweise in der DE 198 34 843 A1 beschrieben und dargestellt.The possibilities for adjusting the valve strokes of the internal combustion engine can be meaningfully supplemented by an additional device for changing the inlet and / or outlet times of the gas exchange valves 2. For this purpose, two camshaft adjusters 56 and 58 are provided on the intake and exhaust side, by means of which the valve timing on the intake and exhaust side of the internal combustion engine can be adjusted to "early" or "late" depending on the operating condition. For this purpose, the two camshaft adjusters 56 and 58 are connected via a 3/2-way valve designed switching valve 60 and 62, each with a first control line 64, 65 to the pressure oil - supply line 52, while in each case a second control line 66, 67 to the oil sump 38 of the internal combustion engine returns. The structure of such camshaft adjuster 56, 58 is for example in the DE 198 34 843 A1 described and illustrated.

In den Figuren 7 bis 14 ist eine konstruktive Umsetzung der Ölversorgung für den variablen Ventiltrieb dargestellt, der im folgenden näher beschrieben ist. Ein Tassenstösselgehäuse 68 weist Öffnungen 70 auf, in denen die einzelnen schaltbaren Tassenstössel 4 Aufnahme finden. Im Gehäuse 68 sind zwei Längsbohrungen 72 und 74 vorgesehen, in denen zur Ausbildung von jeweils zwei Teilölkanälen 72a, 72b und 74a, 74b zwei Formeinlegeteile 76 und 78 eingesetzt sind. In den Formeinlegeteilen 76, 78 sind zur Ausbildung der Teilölkanäle 72a,b und 74a,b jeweils zwei Längsnuten 80a,b und 82a,b eingebracht. Die Formeinlegeteile 76, 78 weisen darüber hinaus über den Umfang verteilte nutenförmige radiale Ausnehmungen 84a bis 84f und 86a bis 86f auf, die mit den Längsnuten 80a,b bzw. 82a,b verbunden sind. Wie insbesondere anhand der Schnittdarstellung in Fig. 10 erkennbar, sind die Ausnehmungen 84, 86 jeweils mit im Gehäuse 68 versehenen Ölkanälen 88, 90 verbunden, die zum Schalten der Tassenstössel 4 zu den in Figur 3 dargestellten Öffnungen 33 führen. Zur Abdichtung der-Formeinlegeteile 76, 78 sind deren stirnseitigen Enden in den Bohrungen 72, 74 verklebt oder es werden separate Abdichtstutzen (nicht dargestellt) an den beiden Enden der Bohrungen eingepresst. Die Formeinlegeteile 76, 78 bestehen vorzugsweise aus demselben Material wie das Tassenstösselgehäuse 68, d.h. aus Aluminium; andere Materialien, wie z.B. Kunststoff sind jedoch ebenso einsetzbar.In the FIGS. 7 to 14 is a constructive implementation of the oil supply for the variable valve train shown, which is described in more detail below. A bucket tappet housing 68 has openings 70, in which the individual switchable tappets 4 record. In the housing 68, two longitudinal bores 72 and 74 are provided, in which two mold inserts 76 and 78 are used to form two partial oil channels 72a, 72b and 74a, 74b. In the Formeinlegeteilen 76, 78, two longitudinal grooves 80a, b and 82a, b are introduced to form the partial oil channels 72a, b and 74a, b. The mold inserts 76, 78 also have circumferentially distributed groove-shaped radial recesses 84a to 84f and 86a to 86f connected to the longitudinal grooves 80a, b and 82a, b, respectively. As in particular with reference to the sectional view in Fig. 10 recognizable, the recesses 84, 86 are each provided with in the housing 68 oil passages 88, 90 connected to the switching of the tappets 4 to the in FIG. 3 lead shown openings 33. To seal the-Formeinlegeteile 76, 78 whose end faces are glued into the holes 72, 74 or there are separate Abdichtstutzen (not shown) pressed at the two ends of the holes. The mold inserts 76, 78 are preferably made the same material as the tappet housing 68, ie aluminum; however, other materials such as plastic are equally applicable.

In der Mitte des Tassenstösselgehäuses 68 sind weiterhin vier Öffnungen 94a bis 94d erkennbar, die zur Aufnahme der vier Schaltventile 36, 42, 46, 50 dienen, die zur besseren Übersicht im Tassenstösselgehäuse 68 selbst nicht eingezeichnet sind. Die Öffnungen 94a bis 94d stehen jeweils mit einem der Teilölkanale 72a,b bzw. 74 a,b in Verbindung, in diesem Fall Öffnung 94a mit Ölkanal 72b, Öffnung 94b mit Ölkanal 74a, Öffnung 94c mit Ölkanal 72a und Öffnung 94d mit Ölkanal 74b. Die in Fig. 7 erkennbaren externen Druckleitungen 96a und 96b dienen dazu, dass der an beiden Öffnungen 94c und 94d zum Schalten der Ventile 36, 42 anliegende Öldruck parallel dazu auch den Öffnungen 94a und 94b zum Schalten der Ventile 46, 50 zugeführt wird.In the middle of the tappet housing 68 four openings 94a to 94d are still visible, which serve to accommodate the four switching valves 36, 42, 46, 50, which are not shown for clarity in the tappet housing 68 itself. The openings 94a to 94d are in each case in communication with one of the partial oil channels 72a, b and 74a, b, in this case opening 94a with oil channel 72b, opening 94b with oil channel 74a, opening 94c with oil channel 72a and opening 94d with oil channel 74b. In the Fig. 7 identifiable external pressure lines 96a and 96b serve that the oil pressure applied to both openings 94c and 94d for switching the valves 36, 42 is also supplied in parallel to the openings 94a and 94b for switching the valves 46, 50.

Claims (5)

  1. Valve drive for an internal combustion engine, having at least two inlet and/or outlet valves per cylinder, which valves can be actuated by means of an inlet and/or outlet camshaft, and having lift transmission elements arranged between the cams of the inlet and/or outlet camshaft and having means for varying the valve lift of the inlet and/or outlet valves, with at least two inlet and/or outlet valves per cylinder interacting with at least two partial cams which have different lift curves, and with the lift transmission elements of said gas exchange valves having at least two lifting elements which in each case interact with the partial cams, and having hydraulic supply lines for the valve lift switch, with the supply lines (34, 44) for the valve lift switch of a first inlet or outlet valve (EV1, AV1) being separate from the supply lines (40, 48) for the valve lift switch of a second inlet or outlet valve (EV2, AV2), so that the first inlet or outlet valve (EV1, AV1) can be switched independently of the second inlet or outlet valve (EV2, AV2), with at least a part of the supply lines (34, 44, 40, 48) being formed as ducts (72a,b, 74a,b) in a bucket tappet housing (68) of the cylinder head, characterized in that at least one bore (72, 74) is provided in the bucket tappet housing (68), in which bore (72, 74) is inserted an insert part (76, 78) in order to form the ducts (72a,b, 74a,b).
  2. Valve drive according to Claim 1, characterized in that the first inlet or outlet valve (EV1, AV1) is assigned a first multi-part cam (6) whose lift curves (hEV1, HEV1 and hAV1, HAV1) differ from the lift curves (hEV2, HEV2 and hAV2, HAV2) of a second multi-part cam (7), with the cam (7) being assigned as a lift transmission element to the second inlet or outlet valves (EV2, AV2).
  3. Valve drive according to Claim 1, characterized in that the insert part (76, 78) has two longitudinal grooves (80a,b, 82a,b), which run substantially over the entire length, and radial recesses (84a-f, 86a-f) which are connected to the longitudinal grooves and which are connected to the oil ducts (72a,b, 74a,b) which lead to the bucket tappets (4).
  4. Valve drive according to one of Claims 1 to 3, characterized in that openings (94a-d) for holding the switching valves (36, 42, 46, 50), by means of which the pressurized oil supply to the oil ducts (72a,b, 74a,b) can be controlled, are provided in the bucket tappet housing (68).
  5. Valve drive according to one of the preceding claims, characterized in that, in addition to the valve lift switch, a camshaft adjuster (56, 58) for varying the inlet and/or outlet times is arranged on the inlet and/or outlet camshaft.
EP02769980A 2001-09-11 2002-08-22 Valve mechanism for an internal combustion engine Expired - Lifetime EP1427918B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10144712 2001-09-11
DE10144712 2001-09-11
DE10212327A DE10212327A1 (en) 2001-09-11 2002-03-20 Induction and exhaust valve mechanism has switching supply lines for first valve separate from those for second valve
DE10212327 2002-03-20
PCT/EP2002/009379 WO2003023197A1 (en) 2001-09-11 2002-08-22 Valve mechanism for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1427918A1 EP1427918A1 (en) 2004-06-16
EP1427918B1 true EP1427918B1 (en) 2008-03-05

Family

ID=26010112

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02769980A Expired - Lifetime EP1427918B1 (en) 2001-09-11 2002-08-22 Valve mechanism for an internal combustion engine

Country Status (5)

Country Link
EP (1) EP1427918B1 (en)
JP (1) JP2005502808A (en)
AT (1) ATE388306T1 (en)
DE (1) DE50211849D1 (en)
WO (1) WO2003023197A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101273186B (en) * 2005-09-27 2010-05-19 丰田自动车株式会社 Variable valve gear and method of adjusting valve opening rate
WO2014165384A1 (en) 2013-04-02 2014-10-09 Eaton Corporation Oil control valve system for valve actuation switching
KR101684559B1 (en) 2015-12-11 2016-12-08 현대자동차 주식회사 Engine provided with continuous varible vavle timing apparatus and continuous varible vavle duration apparatus
GB2552500B (en) * 2016-07-26 2019-11-06 Jaguar Land Rover Ltd Controlling intake valves in an internal combustion engine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1308977C (en) 1986-08-27 1992-10-20 Tsuneo Konno Valve operating device for internal combustion engine
US5431133A (en) * 1994-05-31 1995-07-11 General Motors Corporation Low mass two-step valve lifter
DE19528505A1 (en) 1995-08-03 1997-02-06 Schaeffler Waelzlager Kg Device for selectively actuating at least one gas exchange valve
DE19601587A1 (en) 1996-01-18 1997-07-24 Schaeffler Waelzlager Kg Tappet for a valve train of an internal combustion engine
DE19602013C2 (en) * 1996-01-20 2003-10-30 Ina Schaeffler Kg Cylinder head of an internal combustion engine with a valve train that can be switched to different valve strokes
DE19606054C2 (en) 1996-02-19 1998-07-30 Porsche Ag Valve train of an internal combustion engine
DE19630192C2 (en) 1996-07-26 1998-05-28 Porsche Ag Cylinder head arrangement of an internal combustion engine
DE19834843A1 (en) * 1998-08-01 2000-02-03 Porsche Ag Device for changing the relative rotational position of a shaft to the drive wheel

Also Published As

Publication number Publication date
WO2003023197A1 (en) 2003-03-20
JP2005502808A (en) 2005-01-27
DE50211849D1 (en) 2008-04-17
ATE388306T1 (en) 2008-03-15
EP1427918A1 (en) 2004-06-16

Similar Documents

Publication Publication Date Title
DE69511627T2 (en) Two-stage valve lifter
DE3744343C2 (en)
EP2625395B1 (en) Four-stroke internal combustion engine comprising an engine brake
DE10212327A1 (en) Induction and exhaust valve mechanism has switching supply lines for first valve separate from those for second valve
DE19520117C2 (en) Valve train of an internal combustion engine
DE102012219851B4 (en) Four-stroke engine
DE4206166A1 (en) Variable valve drive with cams driving inner and outer valve stems - has stems coupled by radially sliding pistons in outer stem, engaging inner stem stops during the cam base circle phase
DE19908286B4 (en) Variable valve control for internal combustion engines
WO2012152456A1 (en) Reciprocating internal combustion engine with camshaft adjusting device
DE102016208470A1 (en) Arrangement for the storage of at least one valve drive element
EP0806552B1 (en) Cylinder head for internal combustion engine
DE4210567B4 (en) Variable valve train for a lifting valve of a machine
DE4213856A1 (en) Valve drive for gas exchange valves in IC engines - has two tappets, which are coupled and uncoupled in cam base circle area
EP0723627B1 (en) Valve gear mechanism for a multi-cylinder internal combustion engine
DE102017217500A1 (en) Length adjustable connecting rod with mechanical adjustment
DE19700736B4 (en) Valve gear of an internal combustion engine
WO2018188790A1 (en) Valve mechanism for a longitudinally adjustable connecting rod
EP0455763B1 (en) Hydraulic control device for the valves of a multi-cylinder internal-combustion engine
EP1427918B1 (en) Valve mechanism for an internal combustion engine
DE4318293A1 (en) Drag lever for IC engine poppet valve - combines two pistons longitudinally displaceable between lever and working chamber
DE4411182B4 (en) Switchable valve control for internal combustion engines
DE19519601C2 (en) Valve drive system for a multi-cylinder internal combustion engine
DE4202542A1 (en) Variable lift valve drive - adjusts piston surface area presented to pressure in pressure chamber
DE4124305C2 (en) Valve train for an internal combustion engine
WO1993018284A1 (en) Cylinder head for an internal combustion engine

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20040413

AK Designated contracting states

Kind code of ref document: A1

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

RIN1 Information on inventor provided before grant (corrected)

Inventor name: JOSENHANS, ARMIN

Inventor name: SCHWARZENTHAL, DIETMAR

Inventor name: SPIEGEL, LEO

17Q First examination report despatched

Effective date: 20061211

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE FR GB IT

RBV Designated contracting states (corrected)

Designated state(s): AT DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50211849

Country of ref document: DE

Date of ref document: 20080417

Kind code of ref document: P

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: DR. ING. H.C. F. PORSCHE AKTIENGESELLSCHAFT

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: DR. ING. H.C. F. PORSCHE AKTIENGESELLSCHAFT

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

26N No opposition filed

Effective date: 20081208

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

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

Ref country code: AT

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

Effective date: 20080822

REG Reference to a national code

Ref country code: FR

Ref legal event code: CD

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20110310 AND 20110316

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20110331 AND 20110406

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

Ref country code: GB

Payment date: 20110819

Year of fee payment: 10

Ref country code: FR

Payment date: 20110901

Year of fee payment: 10

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

Ref country code: IT

Payment date: 20110823

Year of fee payment: 10

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

Effective date: 20120822

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130430

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

Ref country code: IT

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

Effective date: 20120822

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

Ref country code: GB

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

Effective date: 20120822

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

Ref country code: FR

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

Effective date: 20120831

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

Ref country code: DE

Payment date: 20160808

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50211849

Country of ref document: DE

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

Ref country code: DE

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

Effective date: 20180301