DE4326331A1 - Valve gear of an internal combustion engine - Google Patents

Valve gear of an internal combustion engine

Info

Publication number
DE4326331A1
DE4326331A1 DE19934326331 DE4326331A DE4326331A1 DE 4326331 A1 DE4326331 A1 DE 4326331A1 DE 19934326331 DE19934326331 DE 19934326331 DE 4326331 A DE4326331 A DE 4326331A DE 4326331 A1 DE4326331 A1 DE 4326331A1
Authority
DE
Germany
Prior art keywords
rocker arm
eccentric
cam
valve
internal combustion
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.)
Ceased
Application number
DE19934326331
Other languages
German (de)
Inventor
Harald Unger
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke 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 DE19924223173 external-priority patent/DE4223173A1/en
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Priority to DE19934326331 priority Critical patent/DE4326331A1/en
Priority to EP93119520A priority patent/EP0638706A1/en
Priority to JP32807293A priority patent/JP3245492B2/en
Priority to US08/176,280 priority patent/US5373818A/en
Publication of DE4326331A1 publication Critical patent/DE4326331A1/en
Ceased legal-status Critical Current

Links

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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • 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
    • 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
    • F01L13/0021—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 by modification of rocker arm ratio
    • F01L13/0026—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 by modification of rocker arm ratio by means of an eccentric
    • 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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/06—Timing or lift different for valves of same cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis

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

An internal combustion engine has at least two inlet valves per cylinder, the lifting curve of which is adjustable differently from one another. The adjustment is performed by means of an eccentric shaft, which displaces the point of support of a transmission element situated between each cam and each valve, the two eccentrics assigned to a cylinder being of different geometry. The transmission element is formed by a rocker arm supported on the eccentric and operated by the cam, which rocker arm in turn acts on a valve lever. The respective contact surfaces are formed by rollers. This is an additional application to patent application P 4223173.6.

Description

Die Erfindung betrifft einen Ventiltrieb einer Brenn­ kraftmaschine mit zumindest zwei parallel wirkenden, je­ weils durch einen Nocken sowie ein Übertragungsglied be­ tätigten Hubventilen je Zylinder, deren Ventilhubverlauf voneinander verschiedenartig verstellbar ist, wozu die Abstützpunkte der Übertragungsglieder über verdrehbare, auf einer gemeinsamen Exzenterwelle liegende Exzenter verstellbar sind und sich die Erhebungskurven der zumin­ dest zwei Exzenter je Zylinder voneinander unterscheiden, nach Patentanmeldung 42 23 173.6. Ein weiteres Vorteil­ haftes Übertragungsglied für einen derartigen Ventiltrieb aufzuzeigen, ist Aufgabe der vorliegenden Erfindung.The invention relates to a valve train of a burner Engine with at least two acting in parallel, each Weil be by a cam and a transmission link actuated lift valves per cylinder, their valve lift curve is adjustable differently from one another, for which the Support points of the transmission links via rotatable, eccentrics lying on a common eccentric shaft are adjustable and the elevation curves of the at distinguish at least two eccentrics per cylinder, after patent application 42 23 173.6. Another benefit adhesive transmission link for such a valve train to demonstrate is the object of the present invention.

Zur Lösung dieser Aufgabe ist vorgesehen, daß das Über­ tragungsglied als ein sich am Exzenter abstützender Schlepphebel, der auf einen Schwinghebel einwirkt, ausge­ bildet ist. Vorteilhafte Aus- und Weiterbildungen sind im abhängigen Anspruch aufgelistet.To solve this problem it is provided that the over support member as a support on the eccentric Rocker arm, which acts on a rocker arm, out forms is. Advantageous training and further education are in dependent claim listed.

Erläutert wird die Erfindung anhand eines bevorzugten Ausführungsbeispieles. Es zeigt The invention is explained on the basis of a preferred one Embodiment. It shows  

Fig. 1 einen Querschnitt durch einen Brennkraftmaschi­ nen-Zylinderkopf mit einem erfindungsgemäßen Ventiltrieb, Fig. 1 shows a cross section through a Brennkraftmaschi NEN cylinder head with a valve gear according to the invention,

Fig. 2 eine perspektivische Ansicht dieses Ventiltrie­ bes für einen einzigen Zylinder, Fig. 2 is a perspective view of this valve bes Trie for a single cylinder,

Fig. 3 diese Ansicht aus einer anderen Perspektive, Fig. 3 this view from a different perspective,

Fig. 4 eine Perspektivdarstellung insbesondere des Übertragungsgliedes, sowie Fig. 4 is a perspective view, in particular of the transmission member, and

Fig. 5 eine Perspektivdarstellung des Schwinghebels, der Bestandteil des Übertragungsgliedes ist. Fig. 5 is a perspective view of the rocker arm, which is part of the transmission member.

In Fig. 1 ist mit der Bezugsziffer 1 ein Zylinderkopf ei­ ner Brennkraftmaschine bezeichnet. Dieser Zylinderkopf erstreckt sich in der Darstellung senkrecht zur Zeichen­ ebene über mehrere Zylinder. Je Zylinder sind zumindest zwei Einlaßkanäle 2 zu einem Brennraum 3 vorhanden, wobei je Einlaßkanal 2 in bekannter Weise ein Hubventil 4 vor­ gesehen ist. Betätigt wird dieses Hubventil 4 durch einen Nocken 5a einer Nockenwelle, wobei der Nocken auf einen Schlepphebel 6 einwirkt, der seinerseits auf einen Schwinghebel 7 wirkt. Im Schwinghebel 7 ist ein hydrauli­ sches Spielausgleichselement 8 gelagert, auf dem sich letztendlich der Schaft des Hubventiles 4 abstützt. Ins gesamt bildet der Schlepphebel 6 sowie der Schwinghebel 7 ein Übertragungsglied 9, mittels dessen der Hubverlauf des Nockens 5a auf das Hubventil 4 übertragen wird.In Fig. 1, reference numeral 1 denotes a cylinder head of an internal combustion engine. This cylinder head extends across several cylinders in the representation perpendicular to the drawing plane. At least two inlet channels 2 to a combustion chamber 3 are provided per cylinder, a lift valve 4 being seen in front of each inlet channel 2 in a known manner. This is operated poppet valve 4 by a cam of a camshaft 5 a, wherein the cam to a cam follower 6 is applied, which in turn acts on a rocking lever. 7 In the rocker arm 7 , a hydraulic calibrating element 8 is supported, on which the stem of the lift valve 4 is ultimately supported. Overall, the rocker arm 6 and the rocker arm 7 form a transmission member 9 , by means of which the stroke profile of the cam 5 a is transmitted to the lift valve 4 .

Wie ersichtlich stützt sich das Übertragungsglied 9 bzw. der Schlepphebel 6 an einem Exzenter 10a ab, der aus ei­ ner Exzenterwelle 10 herausgearbeitet ist. Wird die Ex­ zenterwelle 10 um ihre Längsachse 10b verdreht, so wird der Abstützpunkt des Schlepphebels 6 bzw. des Übertra­ gungsgliedes 9 verschoben. Mit einer derartigen Verände­ rung des Abstützpunktes des Übertragungsgliedes 9 ergeben sich bei gleichem Nockenhub unterschiedliche Ventilhübe, da aufgrund der geänderten Abstützung der Schlepphebel 6 bei Rotation des Nockens 5a gegenüber dem Schwinghebel 7 eine unterschiedliche Bewegungsbahn durchläuft, so daß auch der Schwinghebel 7 unterschiedlich ausgelenkt wird. Insbesondere ist es hiermit möglich, neben einem maxima­ len Ventilhub auch einen Ventilhub nahezu vom Betrag 0 zu erzielen, bei dem das Hubventil 4 lediglich minimal ge­ öffnet wird.As can be seen, the transmission link 9 or the rocker arm 6 is supported on an eccentric 10 a, which is machined out of an eccentric shaft 10 . If the Ex center shaft 10 is rotated about its longitudinal axis 10 b, the support point of the rocker arm 6 or the transmission member 9 is shifted. With such a change tion of the support point of the transmission member 9 there are different valve lifts at the same cam stroke, since due to the changed support of the rocker arm 6 during rotation of the cam 5 a with respect to the rocker arm 7 passes through a different movement path, so that the rocker arm 7 is deflected differently . In particular, it is hereby possible to achieve a valve lift of almost the amount 0 in addition to a maximum valve lift, in which the lift valve 4 is opened only minimally.

Geführt wird der Schlepphebel 6 durch eine in ihrer Ge­ samtheit mit der Bezugsziffer 13 bezeichnete Bolzen-Lang­ loch-Führung. Wie ersichtlich weist der Schlepphebel 6 ein Langloch 13a auf, über welches er in einen Bolzen 13b eingehängt ist, der am Zylinderkopf in einer Lagerstelle 13c befestigt ist. Aufgrund dieser Bolzen-Langloch-Füh­ rung 13 kann somit der Schlepphebel 6 unterschiedliche Positionen einnehmen. Selbstverständlich kann die Bolzen- Langloch-Führung 13 auch umgekehrt ausgebildet sein, d. h. der Bolzen 13b kann am Schlepphebel 6 befestigt sein und das Langloch 13a kann dann in der Zylinderkopf-Lager­ stelle 13c vorgesehen sein. Zur Sicherstellung der be­ schriebenen Verstellfunktion greift ferner an einem Ab­ satz 6a des Schlepphebels ein Rückstelldorn 11 an, der den Schlepphebel 6 stets sowohl gegen den Nocken 5a als auch gegen den Exzenter 10a preßt. Hierzu wird der Rück­ stelldorn 11 in entsprechender Weise von einer Druckfeder 12a beaufschlagt, die sich an einem in den Zylinderkopf 1 eingeschraubten Führungselement 12c abstützt.The rocker arm 6 is guided by a pin-long hole guide designated in its entirety with the reference number 13 . As can be seen, the rocker arm 6 has an elongated hole 13 a, via which it is suspended in a bolt 13 b, which is attached to the cylinder head in a bearing 13 c. Due to this bolt-elongated Füh tion 13 , the rocker arm can take 6 different positions. Of course, the elongated bolt guide 13 can also be designed the other way round, ie the bolt 13 b can be attached to the rocker arm 6 and the elongated hole 13 a can then be provided in the cylinder head bearing 13 c. To ensure be signed adjustment function further comprises a return mandrel 11 engages a rate from 6 a of the rocker arm on which presses the cam follower against the cam 6 always both 5a and against the eccentric 10 a. For this purpose, the return mandrel 11 is acted upon in a corresponding manner by a compression spring 12 a, which is supported on a guide element 12 c screwed into the cylinder head 1 .

Wie die Fig. 2, 3 zeigen, sind für jeden Zylinder bzw. Brennraum 3 des Brennkraftmaschinen-Zylinderkopfes 1 zwei Hubventile 4, 4′ vorgesehen. Jedem Hubventil 4, 4′ ist ein eigener Nocken 5a, 5a′ sowie ein eigenes Übertra­ gungsglied 9, 9′ in Form eines eigenen Schlepphebels 6, 6′ sowie eines eigenen Schwinghebels 7, 7′ zugeordnet. Dabei stützt sich jeder Schlepphebel 6, 6′ an einem eige­ nen Exzenter 10a, 10a′ der sich über den gesamten Zylin­ derkopf 1 erstreckenden Exzenterwelle 10 ab. Wie Fig. 1 zeigt, unterscheiden sich die beiden einem Zylinder bzw. Brennraum 3 zugeordneten Exzenter 10a, 10a′ in ihrer Geo­ metrie. Identisch sind die beiden Exzenter 10a, 10a′ ei­ nes Zylinders/Brennraumes lediglich in den Punkten des minimalen sowie des maximalen Exzenterhubes. In der ge­ zeigten Position minimalen Exzenterhubes bleiben die bei­ den Hubventile 4, 4′ eines Zylinders trotz maximalen Nockenhubes nahezu geschlossen. Wird hingegen ausgehend von der gezeigten Position die Exzenterwelle 10 um 180° gedreht und verstellen somit die Exzenter 10a, 10a′ auf­ grund ihres dann maximalen Exzenterhubes die Schlepphebel 6, 6′ dementsprechend, so werden bei maximalem Nockenhub die beiden Hubventile 4, 4′ maximal geöffnet. In Zwi­ schenpositionen der Exzenterwelle 10 hingegen werden die beiden Hubventile 4, 4′ bei maximalem Nockenhub unter­ schiedlich weit geöffnet. Der Ventilhubverlauf dieser beiden Hubventile 4, 4′ ist somit durch Verstellen der Exzenterwelle 10 voneinander verschiedenartig veränder­ bar.As shown in FIGS. 2, point 3 are provided for each cylinder or combustion chamber 3 of the engine cylinder head 1, two lift valves 4, 4 '. Each lift valve 4 , 4 'has its own cam 5 a, 5 a' and its own transmission member 9 , 9 'in the form of its own rocker arm 6 , 6 ' and its own rocker arm 7 , 7 '. Here, each cam follower 6 6 '10 at a EIGE NEN eccentric 10 a, a' 1 extending eccentric shaft 10 is supported, the The head over the entire Zylin from. As shown in FIG. 1, the two to one cylinder or combustion chamber 3 associated eccentric 10 distinguish a, 10 a 'in their geometry Geo. The two eccentrics 10 a, 10 a 'egg nes cylinder / combustion chamber are identical only in the points of the minimum and maximum eccentric stroke. In the ge shown position minimum eccentric stroke remain almost closed despite the maximum cam stroke at the lift valves 4 , 4 'of a cylinder. If, however, starting from the position shown, the eccentric shaft 10 is rotated by 180 ° and thus adjust the eccentric 10 a, 10 a 'on the basis of their then maximum eccentric stroke, the rocker arm 6 , 6 ' accordingly, the two lift valves 4 , 4 are at maximum cam stroke ′ Opened to the maximum. In inter mediate positions of the eccentric shaft 10, however, the two globe valves 4 , 4 'are opened at different degrees at maximum cam stroke. The valve lift curve of these two lift valves 4 , 4 'is thus different from one another by adjusting the eccentric shaft 10 bar.

Indem das Übertragungsglied 9 durch einen Schlepphebel 6 sowie durch einen nachgeschalteten Schwinghebel 7 gebil­ det wird, ergibt sich eine äußerst zuverlässige Konstruk­ tion, die sich darüber hinaus durch eine raumsparende Bauweise auszeichnet. Um die Reibungsverluste im Ventil­ trieb gering zu halten, ist in den Kontaktbereichen zwi­ schen dem Nocken 5a und dem Schlepphebel 6 sowie zwischen dem Schlepphebel 6 und dem Schwinghebel 7 eine Rollrei­ bung realisiert, d. h. der Schlepphebel 6 trägt eine Rolle 6b und der Schinghebel 7 trägt eine Rolle 7b. By the transmission member 9 is gebil det by a rocker arm 6 and a downstream rocker arm 7 , there is an extremely reliable construction, which is also characterized by a space-saving design. In order to keep the friction losses in the valve low, a rolling friction is realized in the contact areas between the cam 5 a and the rocker arm 6 and between the rocker arm 6 and the rocker arm 7 , ie the rocker arm 6 carries a roller 6 b and the rocker arm 7 carries a role 7 b.

Die Rolle 6b jedes Schlepphebels 6 ist zwischen den bei­ den Armen 6c des abschnittsweise zweiarmig ausgebildeten Schlepphebels geführt und auf einer nicht näher bezeich­ neten, in diesen Schlepphebel-Armen befestigten Rollen­ achse gelagert. Aufgrund der Zweiarmigkeit des Schlepphe­ bels 6 in dem insbesondere aus der Darstellung gemäß Fig. 4 hervorgehenden Abschnitt ist - insbesondere zur Ge­ wichtsreduzierung - auch der diesem Schlepphebel 6 zuge­ ordnete Exzenter 10a zweiteilig ausgebildet, d. h. für jeden der Schlepphebel-Arme 6c ist eine eigene Exzenter­ scheibe vorgesehen, wobei die beiden nebeneinanderliegen­ den, lediglich um die Breite der Rolle 6b voneinander be­ abstandeten Exzenterscheiben selbstverständlich von glei­ cher Konfiguration sind.The role 6 b of each rocker arm 6 is guided between the arms 6 c of the sectioned two-arm rocker arm and axially mounted on a not specified Neten, in these rocker arm arms attached rollers. Due to the two arms of the Schlepphe lever 6 in the particular from the illustration according to FIG. 4 section is - especially for Ge weight reduction - this rocker arm 6 assigned eccentric 10 a formed in two parts, ie for each of the rocker arm 6 c is one own eccentric disc is provided, the two lying next to each other, only by the width of the roller 6 b apart eccentric discs are of course of the same configuration.

Der Schwinghebel 7 weist - wie an sich bekannt - ein Schwinghebel-Lager 7a auf, von dem ausgehend ein Schwing­ hebelarm 7c zu einer Aufnahme 7d führt, die das auf das Hubventil 4 einwirkende hydraulische Spielausgleichsele­ ment 8 trägt. Seitlich am Schwinghebelarm 7c ist die Rolle 7b angeordnet. Mit dieser asymmetrischen Gestal­ tung, die besonders deutlich aus Fig. 5 hervorgeht, er­ gibt sich eine äußerst raumsparende Bauweise. Gelagert ist die Rolle 7b dabei ebenfalls auf einer Achse, die ei­ nerseits am Schwinghebelarm 7c und andererseits an einem weiteren Nebenarm 7e befestigt ist. Dieser Nebenarm 7e führt dabei ebenfalls vom Schwinghebellager 7a zur Auf­ nahme 7d.The rocker arm 7 has - as is known per se - a rocker arm bearing 7 a, from which a rocker arm 7 c leads to a receptacle 7 d, which carries the hydraulic valve compensation element 8 acting on the globe valve 4 . The roller 7 b is arranged on the side of the rocker arm 7 c. With this asymmetrical design, which is particularly clear from Fig. 5, it gives itself an extremely space-saving design. The roller 7 b is also mounted on an axis which is attached to the rocker arm 7 c on the one hand and on the other hand to a further auxiliary arm 7 e. This sidearm 7 e also leads from the rocker support 7 a takeover on the 7 d.

Die gleichen Vorteile hinsichtlich zuverlässiger, einfa­ cher und raumsparender Bauweise, die sich aufgrund der Tatsache einstellen, daß das Übertragungsglied durch den Schlepphebel 6 sowie den Schwinghebel 7 gebildet wird, stellen sich selbstverständlich auch dann ein, wenn die Kontaktflächen sowohl zwischen dem Nocken 5a sowie dem Übertragungsglied 9 als auch innerhalb desselben nicht durch die Rollen 6b, 7b gebildet werden, sondern wenn diese Kontaktflächen als ballige oder gerade Gleitflächen ausgebildet sind. Selbstverständlich sind darüber hinaus eine Vielzahl weiterer Abweichungen insbesondere kon­ struktiver Art vom gezeigten Ausführungsbeispiel möglich, ohne den Inhalt der Patentansprüche zu verlassen.The same advantages in terms of reliable, simple and space-saving design, which arise due to the fact that the transmission link is formed by the rocker arm 6 and the rocker arm 7 , of course, even if the contact surfaces between both the cam 5 a and the transmission member 9 as well as within it are not formed by the rollers 6 b, 7 b, but when these contact surfaces are designed as spherical or straight sliding surfaces. Of course, a large number of further deviations, in particular of a structural type, from the exemplary embodiment shown are possible without departing from the content of the claims.

Claims (2)

1. Ventiltrieb einer Brennkraftmaschine mit zumindest zwei parallel wirkenden, jeweils durch einen Nocken (5a, 5a′) sowie einem Übertragungsglied (9, 9′) be­ tätigten Hubventilen (4, 4′) je Zylinder, deren Ven­ tilhubverlauf voneinander verschiedenartig verstell­ bar ist, wozu die Abstützpunkte der Übertragungs­ glieder (9, 9′) über verdrehbare, auf einer gemein­ samen Exzenterwelle (10) liegende Exzenter (10a, 10a′) verstellbar sind und sich die Erhebungskurven der zumindest zwei Exzenter (10a, 10a′) je Zylinder voneinander unterscheiden, nach Patentanmeldung P 42 23 173.6, dadurch gekennzeichnet, daß das Übertragungsglied (9, 9′) als ein sich am Exzenter (10a, 10a′) ab­ stützender Schlepphebel (6, 6′), der auf einen Schwinghebel (7, 7′) einwirkt, ausgebildet ist.1. Valve train of an internal combustion engine with at least two parallel, each by a cam ( 5 a, 5 a ') and a transmission member ( 9 , 9 ') be operated globe valves ( 4 , 4 ') per cylinder, the Ven tilhub progressively different from each other bar, for which the support points of the transmission members ( 9 , 9 ') via rotatable, on a common eccentric shaft ( 10 ) lying eccentric ( 10 a, 10 a') are adjustable and the elevation curves of the at least two eccentrics ( 10 a, 10 a ′) differ from each other per cylinder, according to patent application P 42 23 173.6, characterized in that the transmission member ( 9 , 9 ′) as a rocker arm ( 6 , 6 ′) supported on the eccentric ( 10 a, 10 a ′) which acts on a rocker arm ( 7 , 7 '), is formed. 2. Ventiltrieb nach Anspruch 1, gekennzeichnet durch zumindest eines der folgenden Merkmale:
  • - der abschnittsweise zweiarmig ausgebildet Schlepphe­ bel (6) trägt eine Rolle (6b), auf der der Nocken (5a) abwälzt
  • - für die beiden Schlepphebelarme (6c) ist jeweils eine eigene Exzenterscheibe vorgesehen
  • - der Schwinghebel (7) trägt eine seitlich am Schwing­ hebelarm (7c), der vom Schwinghebel-Lager (7a) zu einer Aufnahme (7d) für ein Spielausgleichselement (8), auf dem sich das Hubventil (4) abstützt, führt, angeordnete Rolle (7b), auf die der Schlepphebel (6) einwirkt
  • - der Schlepphebel (6) ist über eine Bolzen-Langloch- Führung (13) am Zylinderkopf (1) der Brennkraftma­ schine gelagert, wobei das Langloch (13a) im Schlepphebel (6) oder in der Zylinderkopf-Lager­ stelle (13c) vorgesehen ist.
2. Valve train according to claim 1, characterized by at least one of the following features:
  • - The sectioned two-arm Schlepphe bel ( 6 ) carries a roller ( 6 b) on which the cam ( 5 a) rolls
  • - For the two rocker arm ( 6 c) a separate eccentric is provided
  • - the rocker arm (7) carries a side of the swing arm (7 c) of the rocker bearing (7 a) to a receptacle (7 d) for a play compensation element (8) on which the poppet valve (4) is supported, leads, arranged roller ( 7 b), on which the rocker arm ( 6 ) acts
  • - The rocker arm ( 6 ) is mounted on a bolt slot guide ( 13 ) on the cylinder head ( 1 ) of the internal combustion engine, the slot ( 13 a) in the rocker arm ( 6 ) or in the cylinder head bearing ( 13 c) is provided.
DE19934326331 1992-07-15 1993-08-05 Valve gear of an internal combustion engine Ceased DE4326331A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE19934326331 DE4326331A1 (en) 1992-07-15 1993-08-05 Valve gear of an internal combustion engine
EP93119520A EP0638706A1 (en) 1993-08-05 1993-12-03 Valve actuating mechanism of an internal combustion engine
JP32807293A JP3245492B2 (en) 1993-08-05 1993-12-24 Valve train for internal combustion engine
US08/176,280 US5373818A (en) 1993-08-05 1993-12-30 Valve gear assembly for an internal-combustion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19924223173 DE4223173A1 (en) 1992-07-15 1992-07-15 Valve mechanism for vehicle IC engine - has different lift curves for each pair of valves per cylinder controlled by roller-actuated eccentrics
DE19934326331 DE4326331A1 (en) 1992-07-15 1993-08-05 Valve gear of an internal combustion engine

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DE4326331A1 true DE4326331A1 (en) 1995-02-09

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Cited By (32)

* Cited by examiner, † Cited by third party
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DE19509604A1 (en) * 1995-03-16 1996-09-19 Bayerische Motoren Werke Ag Valve train of an internal combustion engine
EP1039103A2 (en) 1999-03-26 2000-09-27 Bayerische Motoren Werke Aktiengesellschaft Device for modifying the valve lift in an engine cylinder head
EP1143118A2 (en) 2000-04-07 2001-10-10 Bayerische Motoren Werke Aktiengesellschaft Device for varying the valve lift in an engine cylinder head
EP1255027A1 (en) * 2001-05-03 2002-11-06 STS System Technology Services GmbH Mechanic control of variable lift of an intake valve of an internal combustion engine
WO2003008772A1 (en) * 2001-07-17 2003-01-30 Thyssenkrupp Automotive Ag Variable valve-stroke controller
DE10140635A1 (en) * 2001-08-13 2003-04-24 Rudolf Flierl Device for independent variable timing adjustment of gas exchange valves of IC engines has valve lifter and crank shaped to make valve acceleration ratio dependent upon set valve stroke
WO2003078802A1 (en) * 2002-03-18 2003-09-25 Ina-Schaeffler Kg Method and device for controlling the cylinder charge of an externally ignited internal combustion engine
EP1350928A2 (en) * 2002-04-06 2003-10-08 Willi Roth Apparatus for variable actuation of a poppet valve in a combustion engine
EP1387050A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Cylinder head for an internal combustion engine with variable lift valve drive
EP1387049A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Rocker arm for a variable lift valve drive
DE10235401A1 (en) * 2002-08-02 2004-02-12 Bayerische Motoren Werke Ag Lift stroke-variable valve gear for cylinder head of internal combustion engine has second pivoting lever installed stationary on first lever to form one-piece and material uniform double lever arrangement
DE10239909A1 (en) * 2002-08-30 2004-02-26 Audi Ag Variable valve gear especially for reciprocating piston internal combustion engine has adjustment ramp and pre-acceleration ramp forming guide sections of one-sided guide face of slide component for guiding of roller packet
DE10239908A1 (en) * 2002-08-30 2004-02-26 Audi Ag Variable valve gear for reciprocating piston internal combustion engines has cams each operating lift valve via roller packet both of which are commonly movable along adjustment ramp commonly constructed in common slide component
EP1431525A1 (en) * 2002-12-13 2004-06-23 MAHLE Ventiltrieb GmbH Control device for valves in a combustion engine
WO2004057160A1 (en) * 2002-12-21 2004-07-08 Ina-Schaeffler Kg Intermediate lever for a variable valve drive of an internal combustion engine
WO2004059133A1 (en) * 2002-12-27 2004-07-15 Boesl-Flierl Gerlinde Valve actuation device for variable valve control of gas-exchange valves of an internal combustion engine
DE10314683A1 (en) * 2003-03-29 2004-11-11 BÖSL-FLIERL, Gerlinde Variable valve lift control for an internal combustion engine with a camshaft at the bottom
DE10312959A1 (en) * 2003-03-24 2004-11-18 Thyssenkrupp Automotive Ag Device for variable actuation of the gas exchange valves of internal combustion engines and method for operating such a device
DE10323665A1 (en) * 2003-05-14 2004-12-09 Hydraulik-Ring Gmbh Variable valve lift device for internal combustion engine, has rotatable eccentric shaft having eccentrics contours positioned within circle formed by external diameter of bearings of eccentric shaft
DE10359058A1 (en) * 2003-12-17 2005-07-21 Daimlerchrysler Ag Gas exchange valve device for internal combustion engine, has operating unit to cover cam shafts whose rotation angle is adjusted by adjusting device, and valves propelled over cam shafts that are coupled with actuators to operate valves
EP1619361A1 (en) * 2003-05-01 2006-01-25 Yamaha Hatsudoki Kabushiki Kaisha Valve-moving device for engine
EP1619360A1 (en) * 2003-05-01 2006-01-25 Yamaha Hatsudoki Kabushiki Kaisha Valve gear of engine
EP1375847A3 (en) * 2000-12-11 2006-08-23 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable valve drive
EP1710403A1 (en) * 2004-01-30 2006-10-11 HONDA MOTOR CO., Ltd. Engine
EP1801368A1 (en) * 2005-12-26 2007-06-27 Otics Corporation Variable valve operating mechanism
EP1947301A2 (en) * 2003-03-29 2008-07-23 Hydraulik-Ring Gmbh Variable valve lift device for the lift adjustment of gas-exchange valves of an internal combustion engine
DE102007022266A1 (en) 2007-05-09 2008-11-20 Hydraulik-Ring Gmbh Fully-variable valve operating device for stroke setting of charge-cycle valve of internal combustion engine, has camshaft with cam and transmission device is arranged between one of charge-cycle valve and camshaft for stroke setting
DE10312961C5 (en) * 2003-03-24 2009-01-29 Thyssenkrupp Presta Teccenter Ag Device for the variable actuation of gas exchange valves of internal combustion engines
EP1591632A3 (en) * 2004-04-28 2010-09-08 Honda Motor Co., Ltd. Valve train of internal combustion engine
DE102005017064B4 (en) * 2004-04-13 2012-02-09 Mitsubishi Fuso Truck And Bus Corp. Variable valve unit for internal combustion engine
DE102010048708A1 (en) 2010-10-19 2012-04-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve train
EP2630345A1 (en) * 2010-10-19 2013-08-28 Kolbenschmidt Pierburg Innovations GmbH Mechanically controllable valve operating mechanism, and mechanically controllable valve operating mechanism arrangement

Cited By (49)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19509604A1 (en) * 1995-03-16 1996-09-19 Bayerische Motoren Werke Ag Valve train of an internal combustion engine
EP1039103A2 (en) 1999-03-26 2000-09-27 Bayerische Motoren Werke Aktiengesellschaft Device for modifying the valve lift in an engine cylinder head
EP1143118A2 (en) 2000-04-07 2001-10-10 Bayerische Motoren Werke Aktiengesellschaft Device for varying the valve lift in an engine cylinder head
EP1375847A3 (en) * 2000-12-11 2006-08-23 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable valve drive
EP1255027A1 (en) * 2001-05-03 2002-11-06 STS System Technology Services GmbH Mechanic control of variable lift of an intake valve of an internal combustion engine
US6792903B2 (en) 2001-05-03 2004-09-21 Sts System Technology Services Gmbh Mechanical control of the intake valve lift adjustment in an internal combustion engine
WO2003008772A1 (en) * 2001-07-17 2003-01-30 Thyssenkrupp Automotive Ag Variable valve-stroke controller
CN1322227C (en) * 2001-07-17 2007-06-20 泰森克鲁普汽车股份公司 Variable valve-stroke controller
DE10140635A1 (en) * 2001-08-13 2003-04-24 Rudolf Flierl Device for independent variable timing adjustment of gas exchange valves of IC engines has valve lifter and crank shaped to make valve acceleration ratio dependent upon set valve stroke
DE10140635B4 (en) * 2001-08-13 2010-12-02 Entec Consulting Gmbh Device for variable valve lift adjustment of gas exchange valves of an internal combustion engine
WO2003078802A1 (en) * 2002-03-18 2003-09-25 Ina-Schaeffler Kg Method and device for controlling the cylinder charge of an externally ignited internal combustion engine
EP1350928A2 (en) * 2002-04-06 2003-10-08 Willi Roth Apparatus for variable actuation of a poppet valve in a combustion engine
EP1350928A3 (en) * 2002-04-06 2003-12-10 Willi Roth Apparatus for variable actuation of a poppet valve in a combustion engine
EP1387049A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Rocker arm for a variable lift valve drive
DE10235401A1 (en) * 2002-08-02 2004-02-12 Bayerische Motoren Werke Ag Lift stroke-variable valve gear for cylinder head of internal combustion engine has second pivoting lever installed stationary on first lever to form one-piece and material uniform double lever arrangement
EP1387050A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Cylinder head for an internal combustion engine with variable lift valve drive
DE10239908A1 (en) * 2002-08-30 2004-02-26 Audi Ag Variable valve gear for reciprocating piston internal combustion engines has cams each operating lift valve via roller packet both of which are commonly movable along adjustment ramp commonly constructed in common slide component
DE10239909A1 (en) * 2002-08-30 2004-02-26 Audi Ag Variable valve gear especially for reciprocating piston internal combustion engine has adjustment ramp and pre-acceleration ramp forming guide sections of one-sided guide face of slide component for guiding of roller packet
EP1431525A1 (en) * 2002-12-13 2004-06-23 MAHLE Ventiltrieb GmbH Control device for valves in a combustion engine
WO2004057160A1 (en) * 2002-12-21 2004-07-08 Ina-Schaeffler Kg Intermediate lever for a variable valve drive of an internal combustion engine
US7055478B2 (en) 2002-12-21 2006-06-06 Ina-Schaeffler Kg Intermediate lever for a variable valve train of an internal combustion engine
US7044094B2 (en) 2002-12-27 2006-05-16 Gerlinde Bosl-Flierl Valve-lift device for the variable control of gas-exchange valves of an internal combustion engine
WO2004059133A1 (en) * 2002-12-27 2004-07-15 Boesl-Flierl Gerlinde Valve actuation device for variable valve control of gas-exchange valves of an internal combustion engine
DE10312959A1 (en) * 2003-03-24 2004-11-18 Thyssenkrupp Automotive Ag Device for variable actuation of the gas exchange valves of internal combustion engines and method for operating such a device
DE10312961C5 (en) * 2003-03-24 2009-01-29 Thyssenkrupp Presta Teccenter Ag Device for the variable actuation of gas exchange valves of internal combustion engines
DE10312959B4 (en) * 2003-03-24 2006-10-05 Thyssenkrupp Automotive Ag Device for the variable actuation of gas exchange valves of internal combustion engines
US7895981B2 (en) 2003-03-29 2011-03-01 Entec Consulting Gmbh Variable valve lift device for the lift adjustment of gas-exchange valves of an internal combustion engine
DE10314683A1 (en) * 2003-03-29 2004-11-11 BÖSL-FLIERL, Gerlinde Variable valve lift control for an internal combustion engine with a camshaft at the bottom
DE10314683B4 (en) * 2003-03-29 2009-05-07 Entec Consulting Gmbh Variable valve lift control for a combustion engine with a bottom camshaft
EP1947301A2 (en) * 2003-03-29 2008-07-23 Hydraulik-Ring Gmbh Variable valve lift device for the lift adjustment of gas-exchange valves of an internal combustion engine
US7712442B2 (en) 2003-03-29 2010-05-11 Entec Consulting Gmbh Variable valve lift control system for a combustion engine with underneath camshaft
EP1619361A1 (en) * 2003-05-01 2006-01-25 Yamaha Hatsudoki Kabushiki Kaisha Valve-moving device for engine
EP1619360A4 (en) * 2003-05-01 2008-09-17 Yamaha Motor Co Ltd Valve gear of engine
EP1619361A4 (en) * 2003-05-01 2008-11-26 Yamaha Motor Co Ltd Valve-moving device for engine
EP1619360A1 (en) * 2003-05-01 2006-01-25 Yamaha Hatsudoki Kabushiki Kaisha Valve gear of engine
DE10323665A1 (en) * 2003-05-14 2004-12-09 Hydraulik-Ring Gmbh Variable valve lift device for internal combustion engine, has rotatable eccentric shaft having eccentrics contours positioned within circle formed by external diameter of bearings of eccentric shaft
DE10323665B4 (en) * 2003-05-14 2009-02-05 Hydraulik-Ring Gmbh Variable valve lifting device for stroke adjustment of the gas exchange valves of an internal combustion engine
DE10359058A1 (en) * 2003-12-17 2005-07-21 Daimlerchrysler Ag Gas exchange valve device for internal combustion engine, has operating unit to cover cam shafts whose rotation angle is adjusted by adjusting device, and valves propelled over cam shafts that are coupled with actuators to operate valves
EP1710403A1 (en) * 2004-01-30 2006-10-11 HONDA MOTOR CO., Ltd. Engine
US7523727B2 (en) 2004-01-30 2009-04-28 Honda Motor Co., Ltd. Engine
EP1710403A4 (en) * 2004-01-30 2008-12-17 Honda Motor Co Ltd Engine
DE102005017064B4 (en) * 2004-04-13 2012-02-09 Mitsubishi Fuso Truck And Bus Corp. Variable valve unit for internal combustion engine
EP1591632A3 (en) * 2004-04-28 2010-09-08 Honda Motor Co., Ltd. Valve train of internal combustion engine
US7621242B2 (en) 2005-12-26 2009-11-24 Otics Corporation Variable valve operating mechanism
EP1801368A1 (en) * 2005-12-26 2007-06-27 Otics Corporation Variable valve operating mechanism
DE102007022266A1 (en) 2007-05-09 2008-11-20 Hydraulik-Ring Gmbh Fully-variable valve operating device for stroke setting of charge-cycle valve of internal combustion engine, has camshaft with cam and transmission device is arranged between one of charge-cycle valve and camshaft for stroke setting
DE102010048708A1 (en) 2010-10-19 2012-04-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve train
WO2012052217A1 (en) 2010-10-19 2012-04-26 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive
EP2630345A1 (en) * 2010-10-19 2013-08-28 Kolbenschmidt Pierburg Innovations GmbH Mechanically controllable valve operating mechanism, and mechanically controllable valve operating mechanism arrangement

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