EP0434704B1 - Valve-controlled reciprocating piston internal combustion engine - Google Patents

Valve-controlled reciprocating piston internal combustion engine Download PDF

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Publication number
EP0434704B1
EP0434704B1 EP89909562A EP89909562A EP0434704B1 EP 0434704 B1 EP0434704 B1 EP 0434704B1 EP 89909562 A EP89909562 A EP 89909562A EP 89909562 A EP89909562 A EP 89909562A EP 0434704 B1 EP0434704 B1 EP 0434704B1
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EP
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Prior art keywords
valve
valves
inlet
internal combustion
exhaust
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EP89909562A
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German (de)
French (fr)
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EP0434704A1 (en
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Wilhelm Hannibal
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Audi AG
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Audi AG
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    • 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
    • F01L1/265—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 peculiar to machines or engines with three or more intake valves per 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]

Definitions

  • the invention relates to a valve-controlled reciprocating piston internal combustion engine according to the preamble of claim 1.
  • the middle of the three intake or exhaust valves must enclose a smaller angle with the central cylinder axis than the two outer valves, so that all intake and exhaust valves from the cams of an intake or Exhaust camshaft can be operated directly, ie without the intermediary of rocker arms. If the middle valve is an intake valve, it is the first of the three intake valves to be immersed in the cylinder due to its lower inclination. If the middle valve is an exhaust valve, it is the last of the three exhaust valves to emerge from the cylinder.
  • valve pockets In high-compression internal combustion engines, in which the piston crown is almost in the parting plane between the cylinder block and the cylinder head in TDC, this means that a valve pocket must be provided in the piston crown, into which the valve disk of the middle valve can be immersed. If three inlet valves and three outlet valves are provided, such a valve pocket must be provided for the middle inlet valve and for the middle outlet valve, so that the piston is prevented from striking the valve disks of these middle valves.
  • these valve pockets are detrimental to the quality of the combustion, since unburned hydrocarbons can collect in these pockets, which not only reduces the efficiency but also has a negative effect on the exhaust gas composition.
  • Another disadvantage of such valve pockets is that the distance between the first piston ring and the piston crown must be greater than would be required without valve pockets in order to obtain the required height of the top land in the region of the valve pockets, with the result that the piston is longer overall and therefore heavier.
  • the invention has for its object to provide a reciprocating internal combustion engine of the generic type, in which a high compression can be realized without adverse effects on the combustion process and an optimal piston design.
  • the proposal according to the invention ensures that, in an internal combustion engine with three intake valves per cylinder, the central intake valve only begins to open when the piston is already moving downward again.
  • the depth of the valve pocket can be kept smaller than in an internal combustion engine in which all three inlet valves have the same opening start. Even if the opening of the middle intake valve is shifted by a few degrees of the camshaft rotation angle, the depth of the valve pocket is considerably reduced. Possibly. the valve pocket can also be omitted entirely.
  • valve pocket can have a smaller depth than in a machine in which all the outlet valves close at the same time, or, if appropriate, be omitted entirely.
  • the opening times of the three inlet valves or the three outlet valves can be the same, in which case the middle inlet valve closes later and the middle exhaust valve opens earlier.
  • all three intake valves close simultaneously or open all three exhaust valves simultaneously.
  • the cylinder head 1 shown in Figures 1 and 2 has for each cylinder 2, i.e. for each combustion chamber 3, three intake valves 4, 5 and 6 and two exhaust valves 7 and 8.
  • the inlet valves 4, 5 and 6 are actuated by cams 9, 10 and 11 of a common inlet camshaft 12 via bucket tappets 13.
  • the exhaust valves 7 and 8 are actuated via tappets 14 by the cams 15 and 16 of an exhaust camshaft 17.
  • a spark plug bore 18 is provided in the center of the combustion chamber 3.
  • the middle Intake valve 5 includes an angle ⁇ with the longitudinal central axis A, which is smaller than the angle ⁇ between the two outer intake valves 4, 6 and the cylinder central axis A.
  • This smaller inclination of the central intake valve 5 has the result that, with the same control times of the three intake valves 4 , 5 and 6 the middle inlet valve with its valve disk 20 dips into the cylinder 2 earlier than the two outer inlet valves 4 and 6 when opening begins.
  • valve pocket 22 is provided, into which the valve plate 20 can be immersed.
  • this valve pocket affects the quality of the combustion, especially if it has to be relatively deep.
  • the piston 21 must be made longer in order to be able to implement a top land 23 of sufficient width in front of the first piston ring groove 24 in the region of the valve pocket 22.
  • the opening of the middle inlet valve 5 is later than the opening of the two outer inlet valves 4 and 6. This ensures that the middle inlet valve 5 with its valve disk 20 later in the cylinder 2 plunges and only reaches its full opening stroke when the piston 21 has already moved down again from its top dead center. Already a shift of the opening start of the middle inlet valve 5 by a few degrees cam angle rotation angle results in a noticeable reduction in the depth of the valve pocket 22. a valve pocket can be dispensed with at all. The later opening start is achieved by the appropriate position or shape of the cam 10.
  • FIG. 4 A corresponding control diagram is shown in FIG. 4.
  • B is the valve lift curve of the exhaust valves
  • C is the valve lift curve of the outer intake valves 4 and 6
  • D the valve lift curve of the middle inlet valve 5.
  • the opening start a of the two outer inlet valves 4 and 6 is, as usual, in or shortly before TDC, while the inlet start d of the middle inlet valve 5 is shortly after TDC.
  • the inlet cams 9, 10 and 11 have the same shape and only the middle inlet cam is rotated relative to the other two against the direction of rotation R of the inlet camshaft 12, the inlet valve 5 for the middle inlet valve 5 results after the inlet end c of the two outer inlet valves 4 and 6.
  • the middle inlet cam 12 it can also be achieved that the inlet end d of the middle inlet valve 5 coincides with the inlet end c of the two outer inlet valves 4 and 6.
  • FIG. 5 shows the control diagram for such an internal combustion engine with three exhaust valves, E denoting the valve lift curves of the two outer exhaust valves and F denoting the valve lift curve of the middle exhaust valve. While the outlet end f for the two outer outlet valves (curve E) is shortly after TDC as usual, the outlet end e for the middle outlet valve (curve F) is just before TDC.
  • the cam for the middle exhaust valve can be designed so that all three exhaust valves have the same start of exhaust.
  • the control diagram of FIG. 5 is for an internal combustion engine with three exhaust valves and two intake valves, the valve lift curve g for the two intake valves corresponding to the valve lift curve C of FIG. 4. If three inlet valves are provided, the valve lift curve D according to FIG. 4 is selected for the middle inlet valve, at least with regard to the start of opening.
  • the invention also facilitates the use of a variable valve control in which a load and / or speed-dependent rotation is used in particular the intake camshaft is made relative to the crankshaft in order to achieve optimal control times, since the maximum possible adjustment angle of the camshaft depends on the distance between the central intake valve and the piston.

Abstract

In a reciprocating piston internal combustion engine with three inlet valves per cylinder which are individually actuated directly by cams on an inlet camshaft via pushrods and are arranged obliquely to the central cylinder axis, where the central inlet valve is at a smaller angle to the central cylinder axis than the other two, the central inlet valve begins to open later than the other two; thus the valve recess in the piston head for the valve disk of the central inlet valve becomes flatter or altogether inexistent in a high-compression internal combustion engine. Likewise, in an internal combustion engine with three outlet valves, the central outlet valve closes earlier than the other two.

Description

Die Erfindung bezieht sich auf eine ventilgesteuerte Hubkolben-Brennkraftmaschine entsprechend dem Oberbegriff des Anspruchs 1.The invention relates to a valve-controlled reciprocating piston internal combustion engine according to the preamble of claim 1.

Bei derartigen, beispielsweise aus der EP-B 0063385 bekannten Brennkraftmaschinen muß das mittlere der drei Einlaß- oder Auslaßventile mit der Zylinder-Mittelachse einen kleineren Winkel einschließen als die beiden äußeren Ventile, damit alle Einlaß- bzw. Auslaßventile von den Nocken einer Einlaß- bzw. Auslaßnockenwelle direkt, d.h. ohne Zwischenschaltung von Kipphebeln betätigt werden können. Handelt es sich bei dem mittleren Ventil um ein Einlaßventil, so taucht dieses aufgrund seiner geringeren Schrägstellung als erstes der drei Einlaßventile in den Zylinder ein. Ist das mittlere Ventil ein Auslaßventil, so taucht es als letztes der drei Auslaßventile aus dem Zylinder aus. Bei hoch verdichtenden Brennkraftmaschinen, bei denen der Kolbenboden in OT fast in der Teilungsebene zwischen dem Zylinderblock und dem Zylinderkopf liegt, bedeutet dies, daß im Kolbenboden eine Ventiltasche vorgesehen werden muß, in welche der Ventilteller des mittleren Ventils eintauchen kann. Sind drei Einlaßventile und drei Auslaßventile vorgesehen, so muß für das mittlere Einlaßventil und für das mittlere Auslaßventil eine derartige Ventiltasche vorgesehen werden, damit ein Aufschlagen des Kolbens auf die Ventilteller dieser mittleren Ventile vermieden ist. Diese Ventiltaschen sind jedoch für die Güte der Verbrennung schädlich, da sich in diesen Taschen unverbrannte Kohlenwasserstoffe sammeln können, wodurch nicht nur der Wirkungsgrad herabgesetzt, sondern auch die Abgaszusammensetzung negativ beeinflußt wird. Ein weiterer Nachteil derartiger Ventiltaschen besteht darin, daß der Abstand des ersten Kolbenringes vom Kolbenboden größer sein muß, als dies ohne Ventiltaschen erforderlich wäre, um die erforderliche Höhe des Feuersteges im Bereich der Ventiltaschen zu erhalten, was zur Folge hat, daß der Kolben insgesamt länger und dadurch schwerer wird.In such internal combustion engines, for example known from EP-B 0063385, the middle of the three intake or exhaust valves must enclose a smaller angle with the central cylinder axis than the two outer valves, so that all intake and exhaust valves from the cams of an intake or Exhaust camshaft can be operated directly, ie without the intermediary of rocker arms. If the middle valve is an intake valve, it is the first of the three intake valves to be immersed in the cylinder due to its lower inclination. If the middle valve is an exhaust valve, it is the last of the three exhaust valves to emerge from the cylinder. In high-compression internal combustion engines, in which the piston crown is almost in the parting plane between the cylinder block and the cylinder head in TDC, this means that a valve pocket must be provided in the piston crown, into which the valve disk of the middle valve can be immersed. If three inlet valves and three outlet valves are provided, such a valve pocket must be provided for the middle inlet valve and for the middle outlet valve, so that the piston is prevented from striking the valve disks of these middle valves. However, these valve pockets are detrimental to the quality of the combustion, since unburned hydrocarbons can collect in these pockets, which not only reduces the efficiency but also has a negative effect on the exhaust gas composition. Another disadvantage of such valve pockets is that the distance between the first piston ring and the piston crown must be greater than would be required without valve pockets in order to obtain the required height of the top land in the region of the valve pockets, with the result that the piston is longer overall and therefore heavier.

Der Erfindung liegt die Aufgabe zugrunde, eine Hubkolben-Brennkraftmaschine der gattungsgemäßen Art zu schaffen, bei der eine hohe Verdichtung ohne nachteilige Auswirkungen auf den Verbrennungsablauf und eine optimale Kolbengestaltung verwirklicht werden kann.The invention has for its object to provide a reciprocating internal combustion engine of the generic type, in which a high compression can be realized without adverse effects on the combustion process and an optimal piston design.

Diese Aufgabe wird erfindungsgemäß durch die im Kennzeichen des Anspruchs 1 angegebenen Merkmale gelöst.This object is achieved by the features specified in the characterizing part of claim 1.

Durch den erfindungsgemäßen Vorschlag wird erreicht, daß bei einer Brennkraftmaschine mit drei Einlaßventilen pro Zylinder das mittlere Einlaßventil sich erst dann zu öffnen beginnt, wenn sich der Kolben bereits wieder nach unten bewegt. Dadurch kann die Tiefe der Ventiltasche geringer gehalten werden als bei einer Brennkraftmaschine, bei der alle drei Einlaßventile den gleichen Öffnungsbeginn haben. Bereits bei einer Verschiebung des Öffnungsbeginns des mittleren Einlaßventils um wenige Grad Nockenwellen-Drehwinkel ergibt sich eine erhebliche Reduzierung der Tiefe der Ventiltasche. Ggf. kann die Ventiltasche auch ganz entfallen.The proposal according to the invention ensures that, in an internal combustion engine with three intake valves per cylinder, the central intake valve only begins to open when the piston is already moving downward again. As a result, the depth of the valve pocket can be kept smaller than in an internal combustion engine in which all three inlet valves have the same opening start. Even if the opening of the middle intake valve is shifted by a few degrees of the camshaft rotation angle, the depth of the valve pocket is considerably reduced. Possibly. the valve pocket can also be omitted entirely.

Bei einer Brennkraftmaschine mit drei Auslaßventilen wird in analoger Weise durch den früheren Auslaßschluß des mittleren Auslaßventils erreicht, daß sein Ventilteller bereits weitgehend aus dem Zylinder ausgetaucht ist, wenn der Kolben in seinen oberen Totpunkt gelangt. Somit kann auch in diesem Fall die Ventiltasche eine geringere Tiefe haben als bei einer Maschine, bei der alle Auslaßventile gleichzeitig schließen, oder ggf. ganz entfallen.In an internal combustion engine with three exhaust valves, it is achieved in an analogous manner by the earlier exhaust closure of the middle exhaust valve that its valve disk is largely immersed out of the cylinder when the piston reaches its top dead center. Thus, in this case too, the valve pocket can have a smaller depth than in a machine in which all the outlet valves close at the same time, or, if appropriate, be omitted entirely.

Die Öffnungszeiten der drei Einlaßventile bzw. der drei Auslaßventile können gleich sein, in welchem Falle das mittlere Einlaßventil später schließt und das mittlere Auslaßventil früher öffnet. Vorzugsweise schließen jedoch alle drei Einlaßventile gleichzeitig bzw. öffnen alle drei Auslaßventile gleichzeitig.The opening times of the three inlet valves or the three outlet valves can be the same, in which case the middle inlet valve closes later and the middle exhaust valve opens earlier. Preferably, however, all three intake valves close simultaneously or open all three exhaust valves simultaneously.

Ein Ausführungsbeispiel der Erfindung wird im folgenden unter Bezugnahme auf die Zeichnungen bei einer Brennkraftmaschine mit drei Einlaßventilen und zwei Auslaßventilen beschrieben. Es sei jedoch darauf hingewiesen, daß die Erfindung auch bei Brennkraftmaschinen mit drei Einlaßventilen und drei Auslaßventilen und bei Brennkraftmaschinen mit zwei Einlaßventilen und drei Auslaßventilen anwendbar ist. Es zeigt:

  • Figur 1 schematisch eine Teilansicht eines Zylinderkopfes von unten in Richtung der Pfeile 1-1 in Figur 2,
  • Figur 2 einen Schnitt entlang Linie 2-2 in Figur 1,
  • Figur 3 einen Teilschnitt des Zylinderkopfes und des Zylinderblocks in der Ebene des mittleren Einlaßventils,
  • Figur 4 ein Steuerdiagramm der Einlaß- und Auslaßventile der in Figuren 1 und 2 gezeigten Brennkraftmaschine und
  • Figur 5 ein Steuerdiagramm der Einlaß- und Auslaßventile einer Brennkraftmaschine mit drei Auslaßventilen pro Zylinder.
An embodiment of the invention is described below with reference to the drawings in an internal combustion engine with three intake valves and two exhaust valves. However, it should be noted that the invention is also applicable to internal combustion engines with three intake valves and three exhaust valves and to internal combustion engines with two intake valves and three exhaust valves. It shows:
  • 1 schematically shows a partial view of a cylinder head from below in the direction of arrows 1-1 in FIG. 2,
  • FIG. 2 shows a section along line 2-2 in FIG. 1,
  • FIG. 3 shows a partial section of the cylinder head and the cylinder block in the plane of the middle intake valve,
  • Figure 4 is a control diagram of the intake and exhaust valves of the internal combustion engine shown in Figures 1 and 2
  • Figure 5 is a control diagram of the intake and exhaust valves of an internal combustion engine with three exhaust valves per cylinder.

Der in Figuren 1 und 2 dargestellte Zylinderkopf 1 weist für jeden Zylinder 2, d.h. für jeden Brennraum 3, drei Einlaßventile 4, 5 und 6 und zwei Auslaßventile 7 und 8 auf. Die Einlaßventile 4, 5 und 6 werden von Nocken 9, 10 und 11 einer gemeinsamen Einlaßnockenwelle 12 über Tassenstößel 13 betätigt. In entsprechender Weise erfolgt die Betätigung der Auslaßventile 7 und 8 über Tassenstößel 14 durch die Nocken 15 und 16 einer Auslaßnockenwelle 17. In der Mitte des Brennraumes 3 ist eine Zündkerzenbohrung 18 vorgesehen.The cylinder head 1 shown in Figures 1 and 2 has for each cylinder 2, i.e. for each combustion chamber 3, three intake valves 4, 5 and 6 and two exhaust valves 7 and 8. The inlet valves 4, 5 and 6 are actuated by cams 9, 10 and 11 of a common inlet camshaft 12 via bucket tappets 13. In a corresponding manner, the exhaust valves 7 and 8 are actuated via tappets 14 by the cams 15 and 16 of an exhaust camshaft 17. A spark plug bore 18 is provided in the center of the combustion chamber 3.

Damit die drei Einlaßventile 4, 5 und 6 von den Nocken 9, 10 und 11 der Einlaßnockenwelle 12 direkt über Tassenstößel 13 betätigt werden können, ist es erforderlich, daß das mittlere Einlaßventil 5 mit der Längsmittelachse A einen Winkel α einschließt, der kleiner ist als der Winkel β zwischen den beiden äußeren Einlaßventilen 4, 6 und der Zylindermittelachse A. Diese geringere Schrägstellung des mittleren Einlaßventils 5 hat zur Folge, daß bei gleichen Steuerzeiten der drei Einlaßventile 4, 5 und 6 das mittlere Einlaßventil mit seinem Ventilteller 20 beim Öffnungsbeginn früher in den Zylinder 2 eintaucht als die beiden äußeren Einlaßventile 4 und 6. Um dabei ein Aufschlagen des in Figur 3 dargestellten Kolbens 21 auf das mittlere Einlaßventil 5 zu vermeiden, ist im Kolbenboden eine Ventiltasche 22 vorgesehen, in welche der Ventilteller 20 eintauchen kann. Diese Ventiltasche beeinträchtigt jedoch insbesondere dann, wenn sie verhältnismäßig tief sein muß, die Güte der Verbrennung. Außerdem muß der Kolben 21 länger ausgeführt werden, um noch einen Feuersteg 23 ausreichender Breite vor der ersten Kolbenringnut 24 im Bereich der Ventiltasche 22 verwirklichen zu können.So that the three intake valves 4, 5 and 6 can be actuated by the cams 9, 10 and 11 of the intake camshaft 12 directly via tappets 13, it is necessary that the middle Intake valve 5 includes an angle α with the longitudinal central axis A, which is smaller than the angle β between the two outer intake valves 4, 6 and the cylinder central axis A. This smaller inclination of the central intake valve 5 has the result that, with the same control times of the three intake valves 4 , 5 and 6 the middle inlet valve with its valve disk 20 dips into the cylinder 2 earlier than the two outer inlet valves 4 and 6 when opening begins. In order to prevent the piston 21 shown in FIG. 3 from striking the middle inlet valve 5, there is in the piston crown a valve pocket 22 is provided, into which the valve plate 20 can be immersed. However, this valve pocket affects the quality of the combustion, especially if it has to be relatively deep. In addition, the piston 21 must be made longer in order to be able to implement a top land 23 of sufficient width in front of the first piston ring groove 24 in the region of the valve pocket 22.

Um die Tiefe der Ventiltasche 22 möglichst klein halten zu können, ist der Öffnungsbeginn des mittleren Einlaßventils 5 später gelegt als der Öffnungsbeginn der beiden äußeren Einlaßventile 4 und 6. Damit wird erreicht, daß das mittlere Einlaßventil 5 mit seinem Ventilteller 20 später in den Zylinder 2 eintaucht und seinen vollen Öffnungshub erst dann erreicht, wenn sich der Kolben 21 von seinem oberen Totpunkt bereits wieder nach unten bewegt hat. Bereits eine Verschiebung des Öffnungsbeginns des mittleren Einlaßventils 5 um wenige Grad Nockenwinkel-Drehwinkel ergibt eine merkliche Reduzierung der Tiefe der Ventiltasche 22. Ggf. kann auf eine Ventiltasche überhaupt verzichtet werden. Der spätere Öffnungsbeginn wird durch entsprechende Lage oder Form des Nockens 10 erreicht.In order to keep the depth of the valve pocket 22 as small as possible, the opening of the middle inlet valve 5 is later than the opening of the two outer inlet valves 4 and 6. This ensures that the middle inlet valve 5 with its valve disk 20 later in the cylinder 2 plunges and only reaches its full opening stroke when the piston 21 has already moved down again from its top dead center. Already a shift of the opening start of the middle inlet valve 5 by a few degrees cam angle rotation angle results in a noticeable reduction in the depth of the valve pocket 22. a valve pocket can be dispensed with at all. The later opening start is achieved by the appropriate position or shape of the cam 10.

Ein entsprechendes Steuerdiagramm ist in Figur 4 dargestellt. Hierin ist B die Ventilerhebungskurve der Auslaßventile, C die Ventilerhebungskurve der äußeren Einlaßventile 4 und 6 und D die Ventilerhebungskurve des mittleren Einlaßventils 5. Wie ersichtlich, ist der Öffnungsbeginn a der beiden äußeren Einlaßventile 4 und 6 wie üblich in oder kurz vor OT, während der Einlaßbeginn d des mittleren Einlaßventils 5 kurz nach OT liegt. Wenn die Einlaßnocken 9, 10 und 11 die gleiche Form haben und lediglich der mittlere Einlaßnocken gegenüber den beiden anderen entgegen der Drehrichtung R der Einlaßnockenwelle 12 verdreht ist, so ergibt sich für das mittlere Einlaßventil 5 ein Einlaßschluß d, der nach dem Einlaßschluß c der beiden äußeren Einlaßventile 4 und 6 liegt. Durch entsprechende Ausbildung des mittleren Einlaßnockens 12 läßt sich jedoch auch erreichen, daß der Einlaßschluß d des mittleren Einlaßventils 5 mit dem Einlaßschluß c der beiden äußeren Einlaßventile 4 und 6 zusammenfällt.A corresponding control diagram is shown in FIG. 4. Here, B is the valve lift curve of the exhaust valves, C is the valve lift curve of the outer intake valves 4 and 6 and D the valve lift curve of the middle inlet valve 5. As can be seen, the opening start a of the two outer inlet valves 4 and 6 is, as usual, in or shortly before TDC, while the inlet start d of the middle inlet valve 5 is shortly after TDC. If the inlet cams 9, 10 and 11 have the same shape and only the middle inlet cam is rotated relative to the other two against the direction of rotation R of the inlet camshaft 12, the inlet valve 5 for the middle inlet valve 5 results after the inlet end c of the two outer inlet valves 4 and 6. By appropriate design of the middle inlet cam 12, however, it can also be achieved that the inlet end d of the middle inlet valve 5 coincides with the inlet end c of the two outer inlet valves 4 and 6.

Bei einer Brennkraftmaschine mit drei Auslaßventilen wird in analoger Weise der Auslaßschluß des mittleren Auslaßventils früher gelegt als der Auslaßschluß der beiden äußeren Auslaßventile. Dadurch taucht der Ventilteller des mittleren Auslaßventils früher aus dem Zylinder 2 aus, so daß keine oder keine so tiefe Ventiltasche im Kolben vorgesehen werden muß als bei einer Anordnung, bei der alle Auslaßventile gleichzeitig schliessen. Figur 5 zeigt das Steuerdiagramm für eine derartige Brennkraftmaschine mit drei Auslaßventilen, wobei mit E die Ventilerhebungskurven der beiden äußeren Auslaßventile und mit F die Ventilerhebungskurve des mittleren Auslaßventils bezeichnet ist. Während der Auslaßschluß f für die beiden äußeren Auslaßventile (Kurve E) wie üblich kurz nach OT liegt, liegt der Auslaßschluß e für das mittlere Auslaßventil (Kurve F) kurz vor OT. Sind die Nocken für alle drei Auslaßventile identisch und ist nur der das mittlere Auslaßventil betätigenden Nocken in Drehrichtung der Auslaßnockenwelle gegenüber den beiden anderen Nocken verdreht, so ergibt sich naturgemäß ein früherer Auslaßbeginn g für das mittlere Auslaßventil (Kurve F) gegenüber dem Auslaßbeginn h der beiden äußeren Auslaßventile (Kurve E).In an internal combustion engine with three exhaust valves, the exhaust closing of the middle exhaust valve is set earlier than the exhaust closing of the two outer exhaust valves. As a result, the valve plate of the middle exhaust valve emerges from the cylinder 2 earlier, so that no or no valve pocket as deep must be provided in the piston as in an arrangement in which all exhaust valves close simultaneously. FIG. 5 shows the control diagram for such an internal combustion engine with three exhaust valves, E denoting the valve lift curves of the two outer exhaust valves and F denoting the valve lift curve of the middle exhaust valve. While the outlet end f for the two outer outlet valves (curve E) is shortly after TDC as usual, the outlet end e for the middle outlet valve (curve F) is just before TDC. If the cams for all three exhaust valves are identical and only the cam actuating the central exhaust valve is rotated in the direction of rotation of the exhaust camshaft relative to the other two cams, this naturally results in an earlier exhaust start g for the central exhaust valve (curve F) compared to the exhaust start h of the two outer exhaust valves (curve E).

Der Nocken für das mittlere Auslaßventil kann jedoch so ausgelegt werden, daß alle drei Auslaßventile den gleichen Auslaßbeginn haben. Das Steuerdiagramm von Figur 5 ist für eine Brennkraftmaschine mit drei Auslaßventilen und zwei Einlaßventilen, wobei die Ventilerhebungskurve g für die beiden Einlaßventile der Ventilerhebungskurve C von Figur 4 entspricht. Wenn drei Einlaßventile vorgesehen sind, so wird für das mittlere Einlaßventil zumindest hinsichtlich des Öffnungsbeginns die Ventilerhebungskurve D gemäß Figur 4 gewählt.However, the cam for the middle exhaust valve can be designed so that all three exhaust valves have the same start of exhaust. The control diagram of FIG. 5 is for an internal combustion engine with three exhaust valves and two intake valves, the valve lift curve g for the two intake valves corresponding to the valve lift curve C of FIG. 4. If three inlet valves are provided, the valve lift curve D according to FIG. 4 is selected for the middle inlet valve, at least with regard to the start of opening.

Abgesehen von den bereits erwähnten Vorteilen, nämlich Verkleinerung oder Wegfall der Ventiltasche (n) und die Möglichkeit, einen kürzeren und dadurch leichteren Kolben verwenden zu können, erleichtert die Erfindung auch die Anwendung einer variablen Ventilsteuerung, bei der eine last- und/oder drehzahlabhängige Verdrehung insbesondere der Einlaßnockenwelle relativ zur Kurbelwelle zur Erzielung optimaler Steuerzeiten vorgenommen wird, da der maximal mögliche Verstellwinkel der Nockenwelle von dem Abstand zwischen dem mittleren Einlaßventil und dem Kolben abhängig ist.In addition to the advantages already mentioned, namely the reduction or elimination of the valve pocket (s) and the possibility of being able to use a shorter and therefore lighter piston, the invention also facilitates the use of a variable valve control in which a load and / or speed-dependent rotation is used in particular the intake camshaft is made relative to the crankshaft in order to achieve optimal control times, since the maximum possible adjustment angle of the camshaft depends on the distance between the central intake valve and the piston.

Claims (3)

  1. Reciprocating piston internal combustion engine with three inlet and/or exhaust valves (4,5,6) per cylinder (2), which are actuated individually directly over cup tappets (13) by cams (9,10,11) of an intake or exhaust camshaft (12), and are disposed obliquely to the central axis A of the cylinder, the middle one (5) of the three inlet and/or exhaust valve enclosing an angle (α) with the central axis A of the cylinder, which is smaller than the angle enclosed by the two outer valves (4,6) and the central axis A of the cylinder, characterized in that in the case of three inlet valves the middle inlet valve (5) commences to open at a time (b), which is later than the time (a) at which the two outer inlet valves (4,6) commence to open and in the case of three outlet valves the closing phase of the middle exhaust valve is finished at a time "e", which is earlier than the time (f), at which the closing phase of the two outer exhaust valves is finished.
  2. The reciprocating piston internal combustion internal combustion engine of claim 1, characterized in that in the case of three inlet valves the middle inlet valve (5) commences to open at a time (b) after top dead center and that in the case of three outlet valves the closing phase of the middle exhaust valve is finished at a time (e) before top dead center.
  3. The reciprocating piston internal combustion engine of claims 1 and 2, characterized in that in the case of three inlet valves the opening phase is finished at the same time for all inlet valves (4,5,6) and that in the case of three outlet valves the closing phase commences at the same time for all exhaust valves.
EP89909562A 1988-09-17 1989-08-23 Valve-controlled reciprocating piston internal combustion engine Expired - Lifetime EP0434704B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3831733A DE3831733A1 (en) 1988-09-17 1988-09-17 VALVE CONTROLLED PISTON COMBUSTION ENGINE
DE3831733 1988-09-17

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EP0434704A1 EP0434704A1 (en) 1991-07-03
EP0434704B1 true EP0434704B1 (en) 1993-07-21

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4018485A1 (en) * 1990-06-09 1991-12-12 Daimler Benz Ag INTERNAL COMBUSTION ENGINE WITH A THROTTLE VALVE IN A CYLINDER HEAD
DE19624785A1 (en) * 1996-06-21 1998-01-02 Abb Patent Gmbh Multi=valve piston engine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE452640C (en) * 1925-07-10 1927-11-15 Napier & Son Ltd Control for internal combustion engines to drive four or more valves in the cylinder head at an angle to the cylinder axis
DE1243459B (en) * 1965-04-03 1967-06-29 Bayerische Motoren Werke Ag Valve control for internal combustion engines
DE3600408A1 (en) * 1986-01-09 1987-07-16 Audi Ag Reciprocating piston internal combustion engine
DE3524622C2 (en) * 1985-07-10 1988-12-08 Audi Ag, 8070 Ingolstadt, De

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4660529A (en) * 1981-04-22 1987-04-28 Yamaha Hatsudoki Kabushiki Kaisha Four-cycle engine
JPS57176311A (en) * 1981-04-22 1982-10-29 Yamaha Motor Co Ltd Four-cycle engine
JPS60216013A (en) * 1984-04-11 1985-10-29 Yamaha Motor Co Ltd Intake valve mechanism in internal-combustion engine
US4703734A (en) * 1985-03-06 1987-11-03 Nissan Motor Co., Ltd. Multi-valve internal combustion engine
US4667636A (en) * 1985-03-22 1987-05-26 Toyota Jidosha Kabushiki Kaisha Fuel injection type internal combustion engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE452640C (en) * 1925-07-10 1927-11-15 Napier & Son Ltd Control for internal combustion engines to drive four or more valves in the cylinder head at an angle to the cylinder axis
DE1243459B (en) * 1965-04-03 1967-06-29 Bayerische Motoren Werke Ag Valve control for internal combustion engines
DE3524622C2 (en) * 1985-07-10 1988-12-08 Audi Ag, 8070 Ingolstadt, De
DE3600408A1 (en) * 1986-01-09 1987-07-16 Audi Ag Reciprocating piston internal combustion engine

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DE58904986D1 (en) 1993-08-26
EP0434704A1 (en) 1991-07-03
WO1990003498A1 (en) 1990-04-05
DE3831733A1 (en) 1990-03-22

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