EP0197914A1 - Valve control for internal-combustion engines - Google Patents

Valve control for internal-combustion engines Download PDF

Info

Publication number
EP0197914A1
EP0197914A1 EP86890051A EP86890051A EP0197914A1 EP 0197914 A1 EP0197914 A1 EP 0197914A1 EP 86890051 A EP86890051 A EP 86890051A EP 86890051 A EP86890051 A EP 86890051A EP 0197914 A1 EP0197914 A1 EP 0197914A1
Authority
EP
European Patent Office
Prior art keywords
valves
valve
valve control
cylinder
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.)
Granted
Application number
EP86890051A
Other languages
German (de)
French (fr)
Other versions
EP0197914B1 (en
Inventor
Hermann Weichsler
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.)
Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Publication of EP0197914A1 publication Critical patent/EP0197914A1/en
Application granted granted Critical
Publication of EP0197914B1 publication Critical patent/EP0197914B1/en
Expired 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
    • 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
    • F01L1/262—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 valve stems disposed radially from a centre which is substantially the centre of curvature of the upper wall surface of a combustion chamber
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into 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
    • F02F2001/246—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis and orientated radially from the combustion chamber surface

Definitions

  • the invention relates to a valve control for internal combustion engines with at least one row of cylinders, which contains four valves inclined to each other, namely two inlet and two outlet valves opposite each other, the valves being determined by the axes of the opposite valves, approximately on the right Planes crossing angles are rotated by an angle of, for example, 15 to 30 ° with respect to the longitudinal center plane of a row of cylinders or the transverse planes running through the cylinder axes.
  • hemispherical combustion chambers are sought, in which the valves are arranged radially.
  • a hemispherical combustion chamber is not only the cheapest form of the cylinder head in terms of gas exchange, but also enables the required swirl movement of the incoming fresh gas and the placement of the largest possible valves (AT-B -150 188).
  • valve stems protruding beyond the cylinder layout and their spring assemblies are made possible by the nesting of the valve stems in a known manner (AT-B-174 503).
  • valves have previously been actuated via rocker arms, bumpers and angle levers or one or more rocker arms one above the other (DE-B-1 243 459, DE-B-1 300 578).
  • Valve controls of this type are not suitable because of the large oscillating masses for speeds, as are required for high performance motors, since the flutter limit of the valves is too low.
  • the use of stronger valve springs probably offers the possibility of a certain increase in speed, but the spring forces cannot be increased arbitrarily due to the additional load on the valve control.
  • valves on the left and right of the central plane of the cylinder does not permit any larger valve angles, since the valves of adjacent cylinders are obstructed. It is therefore impossible to achieve a hemispherical combustion chamber required for optimal combustion in both constructions.
  • a valve control is known in which the valves of the cylinders are actuated by a total of two camshafts which are provided on the left and right of the engine longitudinal axis.
  • the camshaft is arranged in the plane which is formed by the outer valves, the valve actuation takes place via various rocker arms and / or rocker arms.
  • valves are opened indirectly by means of conical cams, but the cam stroke is transmitted to the valves via heavy rocker arms that are too long for this type of cam and therefore inexact.
  • the valve stems projecting far beyond the cylinder bore also require a cylinder spacing that is no longer common in today's compact engines.
  • the invention is therefore based on the object to avoid the listed disadvantages of known valve controls and to improve valve actuation in the case of fully radial valves in the manner described at the outset so that their advantages can also be exploited for high-speed internal combustion engines without the disadvantages occurring in the prior art to have to accept vibrating transmission organs.
  • the invention solves this problem in that the valves arranged on each side of the longitudinal center plane are assigned two camshafts actuating them, and in that each of the two camshafts is arranged on each side in the valve row and the valve stems formed by valves having the same function.
  • camshafts in the valve control according to the invention doubles compared to the designs for high-performance engines known from the prior art (cf. e.g. DE-B-1 300 578), the invention leads to a reduction in the valve actuation mechanism.
  • the advantage is achieved that rotating shafts, in contrast to reciprocating masses (which are omitted in the invention), do not represent a limitation of the maximum permissible speed.
  • the overall height and the width of the cylinder head are also reduced compared to known solutions.
  • the individual camshafts are driven from the crankshaft in a known manner by a rotating chain (s) or toothed belt; there is also the possibility to achieve the adhesion by means of gears.
  • the conical cams act on tappets.
  • the moving masses are reduced and the valve train no longer forms a speed limit.
  • the bucket tappet is excellently suitable for absorbing lateral forces due to its large diameter and because of its rotational movement additionally achieved by means of an eccentric cam arrangement, and is to be delivered to the cylinder head without loading the valve stem.
  • the transverse forces occurring in the camshaft axis are reduced by means of appropriate camshaft bearings.
  • the conical cam is curved in the elevation region from a plane normal to the axis in the direction of the valve to be actuated.
  • the invention also extends to the fact that the individual cams are axially displaceably mounted on the camshaft for setting the valve play. There is therefore no need to adjust the valve clearance, for example by means of washers between the tappet and the valve stem.
  • a spherical cap-shaped combustion chamber 2 with four valves 3, 4 is provided for each cylinder of a row of cylinders of an internal combustion engine 1. Opposite each other, two valves for controlling the inlet channels 5 running parallel to the cylinder axis are designed as inlet valves 3. The also opposite exhaust valves 4 control the approximately radially opening to the cylinder axis outlet channels 6.
  • the valve stems 3 ', 4' and valve guides 3 ", 4" of all valves 3, 4 are arranged diagonally apart and form a right-angled cross seen in plan view.
  • valves 3, 4 or the cross formed by their shafts 3 ', 4' are rotated by an angle of approximately 15 to 30 °, so that the cylinders are so close to one another unhindered by the valves and their tappets 7 are moved, as is acceptable for accommodating the inlet channels 5 and the accessibility of the spark plug 8 with sufficient wall thicknesses.
  • valve stems 3 ', 4' and the associated tappets 7 of a cylinder engage between the valve stems and tappets of the adjacent cylinder or cylinders without impairing their freedom of movement.
  • two camshafts 9, 10 are arranged on both sides of the longitudinal center plane of the row of cylinders, which is determined in FIG. 1 by the axes of the spark plug threads 8.
  • Each of these camshafts 9 and 10 is placed over a valve series I, 11, 111, IV - (FIG. 2) formed by the nesting of the valves 3, 4 in FIG. 2, in such a way that they are the same through the valves 3, 4 Function arising valve row 1, 11, 111, IV and the valve stems 3 ', 4' formed plane acts.
  • the two outer camshafts 9 therefore actuate the exhaust valves 4, whereas the two camshafts 10 closer to the cylinder axis are assigned to the intake valves 3.
  • valves 3 and 4 of the same function of several cylinders are at an oblique angle in their common plane to the camshafts 9 and 10, they are actuated via tapered cams 11, the cam stroke 12 of which is the oblique angle of the associated valve stem 3 ', 4' is cranked accordingly in order to allow the cam 11 to overflow onto the tappet 7 in the largely central region thereof.
  • the load on the tappet 7 therefore remains centric in every stroke position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

1. Valve control for internal combustion engines with at least one cylinder row, which includes four valves arranged mutually inclined for each cylinder, namely for each two inlet valves and two exhaust valves lying opposite to one another, wherein the planes determined by the axes of the opposed valves are rotated about the cylinder axes through an angle of 15-30 degrees with respect to the longitudinal centre plane of the internal combustion engine or to the transverse planes running through the cylinder axes, and in which there is provided for each a cam shaft on one side of the longitudinal centre plane of the internal combustion engine, which is arranged in the plane of the valves of like function operated thereby, characterised in that the valves (3, 4) arranged on each side of the longitudinal centre plane of the internal combustion engine have associated therewith on each side of this longitudinal centre plane two cam shafts (9, 10) operating them, in that each of the four cam shafts (9, 10) is arranged in one each of the valve rows (I, II, III, IV) formed by the valves (3, 4) of like function operated thereby and the planes formed by their valve stems (3', 4'), and in that the cams (11) of the cam shafts (9, 10) are conically formed and act on the cup tappets (7) operating the valves (3, 4).

Description

Die Erfindung bezieht sich auf eine Ventilsteuerung für Verbrennungskraftmaschinen mit wenigstens einer Zylinderreihe, die je Zylinder vier zueinander geneigte angeordnete Ventile enthält, nämlich jeweis einander gegenüberliegend zwei Ein-und zwei Auslaßventile, wobei die von den Achsen der einander gegenüberliegenden Ventile bestimmten, sich etwa im rechten Winkel kreuzenden Ebenen gegenüber der Längsmittelebene einer Zylinderreihe bzw. den durch die Zylinderachsen laufenden Querebenen um einen Winkel von beispielsweise 15 bis 30° verdreht sind.The invention relates to a valve control for internal combustion engines with at least one row of cylinders, which contains four valves inclined to each other, namely two inlet and two outlet valves opposite each other, the valves being determined by the axes of the opposite valves, approximately on the right Planes crossing angles are rotated by an angle of, for example, 15 to 30 ° with respect to the longitudinal center plane of a row of cylinders or the transverse planes running through the cylinder axes.

Zur Erreichung einer kraftstoffsparenden und - schadstoffarmen Verbrennung werden halbkugelförmige Verbrennungsräume angestrebt, in denen die Ventile radial angeordnet sind. Ein halbkugelförmiger Verbrennungsraum stellt nicht nur die günstigste Form des Zylinderkopfes in Hinblick auf den Gaswechsel dar, sondem ermöglicht in Verbindung mit diametraler Ventilanordnung - (Ventile gleicher Funktion liegen sich räumlich gegenüber) die geforderte Drallbewegung des einströmenden Frischgases und die Unterbringung größtmöglicher Ventile (AT-B-150 188).In order to achieve a fuel-saving and low-pollutant combustion, hemispherical combustion chambers are sought, in which the valves are arranged radially. A hemispherical combustion chamber is not only the cheapest form of the cylinder head in terms of gas exchange, but also enables the required swirl movement of the incoming fresh gas and the placement of the largest possible valves (AT-B -150 188).

Die raumsparende Unterbringung der über den Zylindergrundriß hinausragenden Ventilschäfte und deren Federpakete wird durch die in bekannter Weise vorgenommene Ineinanderschachtelung der Ventilschäfte ermöglicht AT-B-174 503).The space-saving accommodation of the valve stems protruding beyond the cylinder layout and their spring assemblies is made possible by the nesting of the valve stems in a known manner (AT-B-174 503).

Die Betätigung der Ventile erfolgte bisher über Schlepphebel, Stoßstangen und Winkelhebel oder über einen oder mehrere übereinanderliegende Schlepphebel (DE-B-1 243 459, DE-B-1 300 578). Ventilsteuerungen dieser Art sind wegen der großen oszillierenden Massen für Drehzahlen, wie sie bei Hochlei stungsmotoren gefordert werden, nicht geeignet, da die Flattergrenze der Ventile zu niedrig liegt. Die Verwendung stärkerer Ventilfedem bietet wohl die Möglichkeit einer gewissen Drehzahlerhöhung, doch lassen sich die Federkräfte wegen der dadurch erfolgten Mehrbelastung der Ventilsteuerung nicht beliebig erhöhen.The valves have previously been actuated via rocker arms, bumpers and angle levers or one or more rocker arms one above the other (DE-B-1 243 459, DE-B-1 300 578). Valve controls of this type are not suitable because of the large oscillating masses for speeds, as are required for high performance motors, since the flutter limit of the valves is too low. The use of stronger valve springs probably offers the possibility of a certain increase in speed, but the spring forces cannot be increased arbitrarily due to the additional load on the valve control.

Zur Verringerung der aufwendigen Antriebsverbindung zwischen der Nockenwelle und den zueinander geneigt angeordneten Ventilen ist es bekannt, die Nockenwellen kegelförmig auszuführen und unmittelbar auf die Federteller der Ventile einwirken zu lassen (GB-B-226 442). Dabei werden die bei der Verwendung von konischen Nocken auftretenden, in Wellenachse wirkenden Querkräfte über die Ventilführungen abgebaut, was zum sofortigen Verschleiß dieser Bauteile führt.In order to reduce the complex drive connection between the camshaft and the valves arranged at an angle to one another, it is known to design the camshafts in a conical shape and to have them act directly on the spring plates of the valves (GB-B-226 442). The transverse forces that occur in the shaft axis when conical cams are used are reduced via the valve guides, which leads to the immediate wear of these components.

Diesem Umstand Rechnung tragend werden bei einer bekannten Ventilsteuerung für vier radial angeordnete Ventile die Querkräfte durch die Anordnung eines Schlepphebels zwischen konischen Nocken und Ventilschaftende teilweise abgebaut - (DE-B-953 672).Taking this into account, in a known valve control for four radially arranged valves, the lateral forces are partially reduced by the arrangement of a rocker arm between the conical cam and the valve stem end - (DE-B-953 672).

Außerdem läßt die links und rechts der Zylindermittelebene nur einreihige Anordnung der Ventile keine größeren Ventilwinkel zu, da sich die Ventile benachbarter Zylinder behinderten. Die Erreichung eines für optimale Verbrennung geforderten halbkugelförmigen Verbrennungsraumes ist daher bei beiden Konstruktionen unmöglich.In addition, the arrangement of the valves on the left and right of the central plane of the cylinder does not permit any larger valve angles, since the valves of adjacent cylinders are obstructed. It is therefore impossible to achieve a hemispherical combustion chamber required for optimal combustion in both constructions.

Aus der DE-B-1 300 578 ist eine Ventilsteuerung bekannt, bei der die Ventile der Zylinder durch insgesamt zwei Nockenwellen betätigt werden, die links bzw. rechts der Motorlängsachse vorgesehen sind. Obwohl, wie in den Fig. 1 und 2 der DE-B-1 300 578 dargestellt, die Nockenwelle in der Ebene, die durch die äußeren Ventile gebildet wird, angeordnet ist, erfolgt die Ventilbetätigung über verschiedene Schlepp-undloder Kipphebel. Durch die Zwischenschaltung dieser Bauteile wird bei der DE-B-1 300 578 die Übertragung des Nockenhubes auf den räumlich vom zugeordneten Nocken weit entfernten Ventilschaft erst ermöglichtFrom DE-B-1 300 578 a valve control is known in which the valves of the cylinders are actuated by a total of two camshafts which are provided on the left and right of the engine longitudinal axis. Although, as shown in FIGS. 1 and 2 of DE-B-1 300 578, the camshaft is arranged in the plane which is formed by the outer valves, the valve actuation takes place via various rocker arms and / or rocker arms. By interposing these components in DE-B-1 300 578, the transmission of the cam stroke to the valve stem, which is spatially distant from the assigned cam, is only made possible

In der GB-B-375 459 werden radial angeordnete Ventile indirekt mittels konischer Nocken geöffnet, doch wird der Nockenhub über schwere, für diese Nockenart zu lange und somit unexakt arbeitende Kipphebel auf die Ventile übertragen. Die weit über die Zylinderbohrung hinausragenden Ventilschäfte erfordern zudem einen bei heutigen Kompaktmotoren nicht mehr gebräuchlichen Zylinderabstand.In GB-B-375 459, radially arranged valves are opened indirectly by means of conical cams, but the cam stroke is transmitted to the valves via heavy rocker arms that are too long for this type of cam and therefore inexact. The valve stems projecting far beyond the cylinder bore also require a cylinder spacing that is no longer common in today's compact engines.

Der Erfindung liegt somit die Aufgabe zugrunde, die aufgezählten Nachteile bekannter Ventilsteuerungen zu vermeiden und die Ventilbetätigung bei vollradial angeordneten Ventilen in der eingangs beschriebenen Art so zu verbessern, daß ihre Vorteile auch für schnellaufende Verbrennungskraftmaschinen ausgenützt werden können, ohne die beim Stand der Technik auftretenden Nachteile schwingender Übertragungsorgane in Kauf nehmen zu müssen.The invention is therefore based on the object to avoid the listed disadvantages of known valve controls and to improve valve actuation in the case of fully radial valves in the manner described at the outset so that their advantages can also be exploited for high-speed internal combustion engines without the disadvantages occurring in the prior art to have to accept vibrating transmission organs.

Die Erfindung löst die gestellte Aufgabe dadurch, daß den auf jeder Seite der Längsmittelebene angeordneten Ventilen zwei diese betätigende Nockenwellen zugeordnet sind, und daß jede der beiden Nockenwellen auf jeder Seite in der durch Ventile gleicher Funktion gebildeten Ventilreihe und den Ventilschäften gebildeten Ebenen angeordnet ist.The invention solves this problem in that the valves arranged on each side of the longitudinal center plane are assigned two camshafts actuating them, and in that each of the two camshafts is arranged on each side in the valve row and the valve stems formed by valves having the same function.

Obwohl sich bei der erfindungsgemäßen Ventilsteuerung die Anzahl der Nockenwellen gegenüber den aus dem Stand der Technik bekannten (vgl. z.B. DE-B-1 300 578) Konstruktionen für Hochleistungsmotoren verdoppelt, führt die Erfindung zu einer Reduktion der Ventilbetätigungsmechanik. Zusätzlich wird der Vorteil erreicht, daß rotierende Wellen im Gegensatz zu (bei der Erfindung entfallenden) hin-und hergehenden Massen keine Begrenzung der höchstzulässigen Drehzahl darstellen. Ebenso wird die Bauhöhe und die Breite des Zylinderkopfes gegenüber bekannten Lösungsvorschlägen reduziert. Der Antrieb der einzelnen Nockenwellen von der Kurbelwelle aus erfolgt in bekannter Weise durch umlaufende Kette(n) oder Zahnriemen; die Möglichkeit, den Kraftschluß durch Zahnräder zu erreichen, ist ebenfalls gegeben.Although the number of camshafts in the valve control according to the invention doubles compared to the designs for high-performance engines known from the prior art (cf. e.g. DE-B-1 300 578), the invention leads to a reduction in the valve actuation mechanism. In addition, the advantage is achieved that rotating shafts, in contrast to reciprocating masses (which are omitted in the invention), do not represent a limitation of the maximum permissible speed. The overall height and the width of the cylinder head are also reduced compared to known solutions. The individual camshafts are driven from the crankshaft in a known manner by a rotating chain (s) or toothed belt; there is also the possibility to achieve the adhesion by means of gears.

In einer Ausführungsform der Erfindung ist vorgesehen, daß die kegelförmigen Nocken auf Tassenstößel wirken. Durch die Zwischenschaltung von Tassenstößel anstelle schwerer Hebelkonstruktionen zwischen Nocke und Ventilschaft, werden die bewegten Massen verkleinert und der Ventiltrieb bildet somit keine Drehzahlbegrenzung mehr. Der Tassenstößel ist durch seinen großen Durchmesser und wegen seiner durch außermittige Nockenanordnung zusätzlich erreichte Drehbewegung vorzüglich geeignet Querkräfte aufzunehmen und ohne Ventilschaftbelastung an den Zylinderkopf abzugeben. Die in der Nockenwellenachse auftretenden Querkräfte werden über entsprechende Nockenwellenlager abgebaut.In one embodiment of the invention it is provided that the conical cams act on tappets. By interposing bucket tappets instead of heavy lever constructions between the cam and valve stem, the moving masses are reduced and the valve train no longer forms a speed limit. The bucket tappet is excellently suitable for absorbing lateral forces due to its large diameter and because of its rotational movement additionally achieved by means of an eccentric cam arrangement, and is to be delivered to the cylinder head without loading the valve stem. The transverse forces occurring in the camshaft axis are reduced by means of appropriate camshaft bearings.

Weiters kann im Rahmen der Erfindung vorgesehen sein, daß der kegelförmige Nocken im Erhebungsbereich aus einer achsnormalen Ebene in Richtung des zu betätigenden Ventiles gekrümmt ist. Durch die Nockenkrümmung kann bei einer entsprechenden Abstimmung auf die jeweiligen geometrischen Verhältnisse in einfacher Weise erreicht werden, daß der Tassenstößel stets mittig belastet wird, was auch bei vergleichsweise großen Neigungswinkeln zwischen den einzelnen Ventilen eine kippmomentfreie Lagerung der Tassenstößel erlaubt.Furthermore, it can be provided within the scope of the invention that the conical cam is curved in the elevation region from a plane normal to the axis in the direction of the valve to be actuated. With a corresponding adjustment to the respective geometric conditions, the cam curvature can easily achieve that the bucket tappet is always loaded in the center, which allows the bucket tappets to be supported without tilting moment even with comparatively large angles of inclination between the individual valves.

Die Erfindung erstreckt sich auch darauf, daß die einzelnen Nocken auf der Nockenwelle zur Einstellung des Ven tilspieles axial verschiebbar gelagert sind. Es entfällt daher die Notwendigkeit, das Ventilspiel beispielsweise durch Beilagscheiben zwischen Tassenstößel und Ventilschaft einzustellen.The invention also extends to the fact that the individual cams are axially displaceably mounted on the camshaft for setting the valve play. There is therefore no need to adjust the valve clearance, for example by means of washers between the tappet and the valve stem.

In der Zeichnung ist ein nicht beschränkendes Ausführungsbeispiel der Erfindung dargestellt. Es zeigen

  • Figur 1 eine Ventilsteuerung für einen mehrzylindrigen Reihenmotor in schematischer Draufsicht,
  • Figur 2 eine Queransicht der Ventilsteuerung nach Figur 1,
  • Figur 3 einen Längsschnitt durch die Einlaßventilreihe in Schnittebene III der Figur 2 und
  • Figur 4 einen Teillängsschnitt durch die Auslaßventilreihe in Schnittebene IV der Figur 2.
In the drawing, a non-limiting embodiment of the invention is shown. Show it
  • FIG. 1 shows a valve control for a multi-cylinder in-line engine in a schematic plan view,
  • FIG. 2 shows a transverse view of the valve control according to FIG. 1,
  • Figure 3 shows a longitudinal section through the inlet valve row in section plane III of Figure 2 and
  • FIG. 4 shows a partial longitudinal section through the exhaust valve row in section plane IV of FIG. 2.

Für jeden Zylinder einer Zylinderreihe einer Verbrennungskraftmaschine 1 ist ein kugelkalottenförmiger Verbrennungsraum 2 mit je vier Ventilen 3, 4 vorgesehen. Jeweils einander gegenüberliegend sind zwei Ventile für die Steuerung der parallel zur Zylinderachse verlaufenden Einlaßkanäle 5 als Einlaßventile 3 ausgebildet. Die ebenfalls einander gegenüberliegenden Auslaßventile 4 steuern die etwa radial zur Zylinderachse ausmündenden Auslaßkanäle 6. Die Ventilschäfte 3', 4' und Ventilführungen 3", 4" aller Ventile 3, 4 sind schräg auseinanderstrebend angeordnet und bilden in Draufsicht gesehen ein rechtwinkeliges Kreuz.A spherical cap-shaped combustion chamber 2 with four valves 3, 4 is provided for each cylinder of a row of cylinders of an internal combustion engine 1. Opposite each other, two valves for controlling the inlet channels 5 running parallel to the cylinder axis are designed as inlet valves 3. The also opposite exhaust valves 4 control the approximately radially opening to the cylinder axis outlet channels 6. The valve stems 3 ', 4' and valve guides 3 ", 4" of all valves 3, 4 are arranged diagonally apart and form a right-angled cross seen in plan view.

Gegenüber der Längsmittelebene der Zylinderreihe sind die Ventile 3, 4 bzw. das von deren Schäften 3', 4' gebildete Kreuz um einen Winkel von etwa 15 bis 30° verdreht, so daß die Zylinder ungehindert von den Ventilen und deren Tassenstößel 7 so eng aneinander gerückt sind, wie dies zur Unterbringung der Einlaßkanäle 5 und der Zugängiichkeit der Zündkerze 8 bei genügenden Wandstärken vertretbar ist.Compared to the longitudinal center plane of the row of cylinders, the valves 3, 4 or the cross formed by their shafts 3 ', 4' are rotated by an angle of approximately 15 to 30 °, so that the cylinders are so close to one another unhindered by the valves and their tappets 7 are moved, as is acceptable for accommodating the inlet channels 5 and the accessibility of the spark plug 8 with sufficient wall thicknesses.

Die Ventilschäfte 3', 4' und die dazugehörigen Tassenstößel 7 eines Zylinders greifen dabei zwischen die Ventilschäfte und Tassenstößel des bzw. der jeweils benachbarten Zylinder ein, ohne diese in ihrer Bewegungsfreiheit zu beeinträchtigen.The valve stems 3 ', 4' and the associated tappets 7 of a cylinder engage between the valve stems and tappets of the adjacent cylinder or cylinders without impairing their freedom of movement.

Zur Steuerung der Ventile sind zu beiden Seiten der Längsmittelebene der Zylinderreihe, die in Figur 1 durch die Achsen der Zündkerzengewinde 8 bestimmt ist, je zwei Nockenwellen 9, 10 angeordnet.To control the valves, two camshafts 9, 10 are arranged on both sides of the longitudinal center plane of the row of cylinders, which is determined in FIG. 1 by the axes of the spark plug threads 8.

Jede dieser Nockenwellen 9 und 10 wird über eine durch die Ineinanderschachtelung der Ventile 3, 4 in Figur 2 gebildeten Ventilreihen I, 11, 111, IV - (Figur 2) gelegt und zwar derart, daß sie in der durch die Ventile 3, 4 gleicher Funktion entstehenden Ventilreihe 1, 11, 111, IV und den Ventilschäften 3', 4' gebildeten Ebene wirkt. Es betätigen daher die beiden äußeren Nockenwellen 9 die Auslaßventile 4, wogegen die beiden der Zylinderachse näheren Nockenwellen 10 den Einlaßventilen 3 zugeordnet sind.Each of these camshafts 9 and 10 is placed over a valve series I, 11, 111, IV - (FIG. 2) formed by the nesting of the valves 3, 4 in FIG. 2, in such a way that they are the same through the valves 3, 4 Function arising valve row 1, 11, 111, IV and the valve stems 3 ', 4' formed plane acts. The two outer camshafts 9 therefore actuate the exhaust valves 4, whereas the two camshafts 10 closer to the cylinder axis are assigned to the intake valves 3.

Da die Ventile 3 bzw. 4 gleicher Funktion mehrerer Zylinder (vgl. Figur 3 und Figur 4) in ihrer gemeinsamen Ebene zur Nockenwelle 9 bzw. 10 in einem schrägen Winkel stehen, erfolgt ihre Betätigung über kegelig geschliffene Nocken 11, deren Nockenhub 12 dem Schrägwinkel des zugeordneten Ventilschaftes 3', 4' entsprechend gekröpft ist, um das Überlaufen des Nockens 11 auf den Tassenstößel 7 im weitestgehend mittigen Bereich desselben zu ermöglichen. Die Belastung der Tassenstößel 7 bleibt daher in jeder Hublage zentrisch.Since the valves 3 and 4 of the same function of several cylinders (see FIGS. 3 and 4) are at an oblique angle in their common plane to the camshafts 9 and 10, they are actuated via tapered cams 11, the cam stroke 12 of which is the oblique angle of the associated valve stem 3 ', 4' is cranked accordingly in order to allow the cam 11 to overflow onto the tappet 7 in the largely central region thereof. The load on the tappet 7 therefore remains centric in every stroke position.

Claims (4)

1. Ventilsteuerung für Verbrennungskraftmaschinen mit wenigstens einer Zylinderreihe, die je Zylinder vier zueinander geneigt angeordnete Ventile enthält, nämlich jeweils einander gegenüberliegend zwei Ein-(3) und zwei Auslaßventile (4), wobei die von den Achsen der sich gegenüberliegenden Ventile bestimmten Ebenen gegenüber der Längsmittelebene bzw. den durch die Zylinderachsen laufenden Querebenen um einen Winkel von 15 -30° um die Zylinderachsen gedreht sind, dadurch gekennzeichnet, daß den auf jeder Seite der Längsmittelebene angeordneten Ventilen (3, 4) zwei diese betätigende Nockenwellen (9, 10) zugeordnet sind, und daß jede der beiden Nockenwellen (9, 10) auf jeder Seite in der durch Ventile (3, 4) gleicher Funktion gebildeten Ventilreihe (I, II, 111, IV) und den Ventilschäften (3', 4') gebildeten Ebenen angeordnet ist.1. Valve control for internal combustion engines with at least one row of cylinders, which contains four valves inclined to each other, namely opposite each other two inlet (3) and two outlet valves (4), the planes determined by the axes of the opposing valves compared to the The longitudinal center plane or the transverse planes passing through the cylinder axes are rotated by an angle of 15-30 ° around the cylinder axes, characterized in that the valves (3, 4) arranged on each side of the longitudinal center plane are assigned two camshafts (9, 10) actuating them and that each of the two camshafts (9, 10) on each side in the valve row (I, II, 111, IV) formed by valves (3, 4) of the same function and the valve stems (3 ', 4') formed planes is arranged. 2. Ventilsteuerung nach Anspruch 1, dadurch gekennzeichnet, daß die kegelförmigen Nocken (11) auf Tassenstößel (7) wirken.2. Valve control according to claim 1, characterized in that the conical cams (11) act on the tappet (7). 3. Ventilsteuerung nach Anspruch 2, dadurch gekennzeichnet, daß der kegelförmige Nocken (11) im Erhebungsbereich (12) aus einer achsnormalen Ebene in Richtung des zu betätigenden Ventiles (3, 4) gekrümmt ist.3. Valve control according to claim 2, characterized in that the conical cam (11) is curved in the elevation region (12) from an axis-normal plane in the direction of the valve (3, 4) to be actuated. 4. Ventilsteuerung nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß die einzelnen Nocken (11) auf der Nockenwelle (9, 10) zur Einstellung des Ventilspieles axial verschiebbar gelagert sind.4. Valve control according to claim 2 or 3, characterized in that the individual cams (11) on the camshaft (9, 10) are axially displaceably mounted for adjusting the valve clearance.
EP86890051A 1985-03-18 1986-03-10 Valve control for internal-combustion engines Expired EP0197914B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT795/85 1985-03-18
AT79585A AT399021B (en) 1985-03-18 1985-03-18 VALVE CONTROL FOR INTERNAL COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0197914A1 true EP0197914A1 (en) 1986-10-15
EP0197914B1 EP0197914B1 (en) 1988-05-25

Family

ID=3499941

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86890051A Expired EP0197914B1 (en) 1985-03-18 1986-03-10 Valve control for internal-combustion engines

Country Status (3)

Country Link
EP (1) EP0197914B1 (en)
AT (1) AT399021B (en)
DE (1) DE3660224D1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0235121A1 (en) * 1986-02-20 1987-09-02 Hermann Weichsler Internal combustion engine
US4942857A (en) * 1988-01-18 1990-07-24 Yamaha Hatsudoki Kabushiki Kaisha Combustion chamber for engine with multiple valves
FR2740171A1 (en) * 1995-10-18 1997-04-25 Debs Sylvain Valve actuating system, for IC engines

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB375459A (en) * 1931-04-07 1932-06-30 Frank Albert George Butters Improvements in or relating to the valve mechanism of internal combustion engines
GB1152805A (en) * 1966-08-13 1969-05-21 Bayerische Motoren Werke Ag Cylinder Head for Internal Combustion Engine
EP0117850A1 (en) * 1983-02-24 1984-09-05 Mario Anfusio Internal combustion engine of the reciprocating piston-type with multiple-valve cylinders
EP0155261A2 (en) * 1984-03-14 1985-09-18 Hermann Weichsler Valve timing gear for an internal-combustion engine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB226442A (en) * 1924-06-12 1924-12-24 Montague Stanley Napier Improvements in or relating to internal combustion engines
AT150188B (en) * 1935-12-20 1937-07-10 Ludwig Apfelbeck Cylinder head for mixture-compressing four-stroke internal combustion engines.
AT174503B (en) * 1950-04-28 1953-04-10 Ludwig Apfelbeck Internal combustion engine
DE953672C (en) * 1952-05-07 1956-12-06 Daimler Benz Ag Valve control for internal combustion engines
DE1243456B (en) * 1966-03-24 1967-06-29 Paul Icking Device for weight-dosed feeding of animals
DE1300578B (en) * 1966-12-24 1969-08-07 Bayerische Motoren Werke Ag Valve control for internal combustion engines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB375459A (en) * 1931-04-07 1932-06-30 Frank Albert George Butters Improvements in or relating to the valve mechanism of internal combustion engines
GB1152805A (en) * 1966-08-13 1969-05-21 Bayerische Motoren Werke Ag Cylinder Head for Internal Combustion Engine
EP0117850A1 (en) * 1983-02-24 1984-09-05 Mario Anfusio Internal combustion engine of the reciprocating piston-type with multiple-valve cylinders
EP0155261A2 (en) * 1984-03-14 1985-09-18 Hermann Weichsler Valve timing gear for an internal-combustion engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0235121A1 (en) * 1986-02-20 1987-09-02 Hermann Weichsler Internal combustion engine
US4942857A (en) * 1988-01-18 1990-07-24 Yamaha Hatsudoki Kabushiki Kaisha Combustion chamber for engine with multiple valves
FR2740171A1 (en) * 1995-10-18 1997-04-25 Debs Sylvain Valve actuating system, for IC engines

Also Published As

Publication number Publication date
ATA79585A (en) 1994-07-15
EP0197914B1 (en) 1988-05-25
DE3660224D1 (en) 1988-06-30
AT399021B (en) 1995-03-27

Similar Documents

Publication Publication Date Title
DE10148177B4 (en) Valve train with valve lift switching for the gas exchange valves of a 4-stroke internal combustion engine
DE4223172C1 (en) Cylinder head for IC engine - bearing cover for cam shaft bearing also acts for bearing for eccentric shaft
DE68927359T2 (en) Cylinder head for multi-cylinder internal combustion engines
DE69027032T2 (en) Camshaft arrangement for a multi-valve internal combustion engine
DE19815112A1 (en) Arrangement for variable valve timing and valve actuation
DE69017614T2 (en) Cylinder head and valve arrangement for multi-valve internal combustion engine.
DE69314439T2 (en) Valve train for an internal combustion engine
DE10228022A1 (en) Valve lifting device for the stroke adjustment of the gas exchange valves of an internal combustion engine
DE69101185T2 (en) Control device, in particular for an internal combustion engine with a number of valves per cylinder.
DE10303749A1 (en) Overhead valve train for an engine with three valves and a camshaft
EP0155261A2 (en) Valve timing gear for an internal-combustion engine
DE10239224B4 (en) Valve drive for double camshaft motor with three valves
DE69016289T2 (en) Valve drive device for an internal combustion engine.
DE69016709T2 (en) Valve and spring arrangement for an internal combustion engine.
AT399021B (en) VALVE CONTROL FOR INTERNAL COMBUSTION ENGINES
EP0353543B1 (en) Valve-operating device for internal-combustion engines
EP1680577B1 (en) Valve train of an internal combustion engine comprising at least one camshaft
EP0736133B1 (en) Multi-cylinder internal-combustion engine
DE3888817T2 (en) Valve control device for multi-valve internal combustion engine.
DE3624107A1 (en) INTERNAL COMBUSTION ENGINE
EP2209972A1 (en) Device for controlling the residual gas content of cylinders of an internal combustion engine
DE10055595A1 (en) The cylinder shutoff has cylinders with gas exchange valves, cam shaft, driven by crank shaft, two cams, and valve drive element
DE19718710C2 (en) Internal combustion engine with double valve
EP1573178B1 (en) Method for varying valve timing of an internal combustion engine
DE3402605A1 (en) Valve control for a reciprocating piston 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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19861219

17Q First examination report despatched

Effective date: 19870728

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

ITF It: translation for a ep patent filed
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3660224

Country of ref document: DE

Date of ref document: 19880630

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
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19900331

Year of fee payment: 5

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: GB

Effective date: 19910310

REG Reference to a national code

Ref country code: FR

Ref legal event code: AR

REG Reference to a national code

Ref country code: FR

Ref legal event code: BR

GBPC Gb: european patent ceased through non-payment of renewal fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19920120

Year of fee payment: 7

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

Ref country code: DE

Payment date: 19921203

Year of fee payment: 7

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

Ref country code: FR

Effective date: 19931130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: DE

Effective date: 19960903

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;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050310