EP0615058A1 - Cylinder head for an internal combustion engine - Google Patents

Cylinder head for an internal combustion engine Download PDF

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Publication number
EP0615058A1
EP0615058A1 EP94101746A EP94101746A EP0615058A1 EP 0615058 A1 EP0615058 A1 EP 0615058A1 EP 94101746 A EP94101746 A EP 94101746A EP 94101746 A EP94101746 A EP 94101746A EP 0615058 A1 EP0615058 A1 EP 0615058A1
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EP
European Patent Office
Prior art keywords
cylinder head
group
valves
valve
gas exchange
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Granted
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EP94101746A
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German (de)
French (fr)
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EP0615058B1 (en
Inventor
Willi Schultz
Joachim Dr. Esch
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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    • 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
    • F02F3/00—Pistons 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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 cylinder head for an internal combustion engine according to the preamble of claim 1.
  • US Pat. No. 4,637,356 discloses a valve drive with three intake valves actuated by a camshaft, the middle valves of which are actuated directly via bucket tappets with the interposition of a rocker arm and the two external valves.
  • each intake port is assigned its own intake manifold provided with a throttle valve and an injection valve.
  • a single, external inlet valve is actuated in a first operating range.
  • the throttle valves and injectors of the second and third intake valves are actuated in succession.
  • the invention has for its object to provide a cylinder head for an internal combustion engine with improved power and torque values.
  • a gas exchange valve arranged in the circumferential direction of each cylinder is arranged permanently with the interposition of an actuating lever and the other valves of this group are actuated temporarily, this cylinder head is optimized with regard to the gas exchange and delivers an increased power and torque yield.
  • the permanently operated valve enables a space-saving arrangement on the edge of a combustion chamber.
  • the thereby achieved Tangential inflow causes a targeted, rotating charge movement ("Swirl").
  • the radial arrangement of this valve makes it possible to make the one or more valves of the first group comparatively large and thus to achieve an optimal gas throughput for high outputs.
  • valves can be switched on and off using switching mechanisms.
  • These mechanisms can be designed in a variety of ways, for example as a switching device integrated in a hydraulic tappet according to DE-40 27 630 C or as the corresponding cams coupling or uncoupling devices according to DE-41 00 763 A and are therefore not explained in more detail.
  • the permanently operated gas exchange valve which is designed as an inlet valve, is assigned a first separate intake manifold and another valve of this group.
  • the geometry of the intake manifolds can thus be adapted to the different requirements of a low-load or a high-load operation.
  • cylinder head is operated on a spark-ignited internal combustion engine
  • corresponding intake and fuel devices are assigned to these intake manifolds, and a shaft arranged centrally in the cylinder head above each cylinder serves to receive a spark plug.
  • this shaft instead accommodates the device for supplying fuel.
  • the internal combustion engine can be operated at low loads in a fuel-saving manner with only one first inlet valve, which is comparatively small in diameter.
  • An outlet valve of the second group can also be provided with a switching mechanism.
  • the internal combustion engine can then be operated as a two-valve engine be, whereby only a low drive power is required for the valve train. With increasing loads, the two further inlet valves and the second outlet valve are then switched on simultaneously or in succession.
  • the gas throughput then takes place essentially via the comparatively large additional valves, so that the internal combustion engine can then be regarded as a performance-optimized 4-valve engine.
  • the angular positions of the central longitudinal axes of the gas exchange valves are selected so that the combustion chamber roof is as smooth as possible without fissures. Knocking combustion is thereby largely avoided and the knock limit is shifted in the direction of higher power yield.
  • a multi-cylinder internal combustion engine has a cylinder head 1 provided with gas exchange channels with an inserted bearing frame 2.
  • the ducts are designed as inlet ducts 3, 4, 5, which extend from pipe connections provided with injection valves 6 and designed as intake manifolds 7 to a combustion chamber 8.
  • the level L extends from the combustion chamber 8, exhaust channels 9, 10 to a wall 11 of the cylinder head 1.
  • the inlet and outlet channels 3, 4, 5 and 9, 10 are dominated by a first and second group of gas exchange valves, which are designed as inlet and outlet valves 12, 13, 14 and 15, 16, respectively.
  • the intake valves 12, 13 and 14 are arranged along a circumferential direction of each cylinder.
  • the bearing frame 2 has bearings 17, 18 for only schematically shown camshafts, a first camshaft designed as an intake camshaft 19 being mounted in first bearings 17 and a corresponding exhaust camshaft 20 being mounted in the second bearings 18.
  • the first inlet valve 12 is moved with the interposition of an actuating lever provided with a roller 21 and designed as a rocking lever 22 by the inlet camshaft 19, which opens and closes the second and third inlet valves 13, 14 by means of bucket tappets 23.
  • the tappets 23 are slidably mounted in receptacles 24 of the bearing frame 2.
  • the two exhaust valves 15 and 16 are also actuated directly by the exhaust camshaft 20 by means of bucket tappets 23.
  • the first inlet valve 12 is permanently actuated in all operating points of the internal combustion engine and ensures a tangential inflow into the combustion chamber 8, as a result of which a targeted charge movement is achieved.
  • the further inlet valves 13, 14 and an outlet valve 16 can optionally be coupled to the camshafts 19, 20 by means of hydraulic switching mechanisms (not shown) integrated in the tappets 23.
  • the intake valves 13, 14 and the second exhaust valve 16 are shut down. With increasing load, the valves that were initially switched off are then switched on in succession.
  • All gas exchange valves are designed as poppet valves, the diameter D of the first inlet valve 12 being smaller than that of the other valves.
  • the inlet duct 3 assigned to the first inlet valve 12 is connected to a first intake manifold 7, which has an injection valve 6.
  • the further inlet channels 4 and 5 are jointly connected to a second intake pipe 7, which also has an injection valve 6.
  • the intake pipes 7 are detachably held on an outer wall 26 of the cylinder head 1.
  • a shaft 30 is formed centrally in the cylinder head 1 or bearing frame 2 above each cylinder, which opens into the combustion chamber 8 with an opening 31 and is cut by the longitudinal center plane L.
  • a spark plug 32 is inserted into this opening 31 as an ignition device.
  • All gas exchange valves move along their central longitudinal axes, the inlet valves 12, 13, 14 being arranged in such a way that their central longitudinal axes 33, 34, 35 intersect a combustion chamber roof 36 in such a way that the intersection points 37 which arise in this case have a different distance A1, A2 and A3 to the central longitudinal plane L.
  • the central longitudinal axes 33 and 34 of the first and second inlet valves 12 and 13 run parallel to one another, the central longitudinal axis 33 including an angle 38 with the central longitudinal plane L, which is smaller than the corresponding angle 39 of the central longitudinal axis 35 of the third inlet valve 14.
  • the central longitudinal axes 40 assigned to the exhaust valves 15 and 16 and those of the intake valves 13 and 14 each cut longitudinal axes 41 of the camshafts 19, 20.
  • the rocker arm 22 has a hydraulic valve clearance compensation element 42, which is supplied with pressure oil via bores 43.
  • This lever 22 is rotatably mounted on an axis 44, which is on the one hand in a bearing arm 45 of the frame 2 is held.
  • a feed bore 46 runs in this arm 45 for supplying the compensating element 42 and for lubricating the rocker arm 22.

Abstract

The cylinder head of an internal combustion engine has three inlet valves on one side of a longitudinal central plane (L) and two outlet valves on the other side. The inlet valves are arranged in a circumferential direction of a cylinder of the internal combustion engine and a first inlet valve which is arranged near to the edge of a combustion space is permanently driven by a cam shaft with intermediate connection of a space-saving actuation lever (22). The other inlet valves are connected into the circuit successively or simultaneously depending on requirements. A fuel-saving change of charge can be achieved under low load by the first inlet valve being subjected to a tangential inflow whilst under increased load requirement and optimised throughput of gas over the valves connected into the circuit is possible. <IMAGE>

Description

Die Erfindung betrifft einen Zylinderkopf für eine Brennkraftmaschine gemäß dem Oberbegriff des Patentanspruches 1.The invention relates to a cylinder head for an internal combustion engine according to the preamble of claim 1.

US-PS 4 637 356 offenbart einen Ventilantrieb mit drei von einer Nockenwelle betätigten Einlaßventilen, deren mittleres unter Zwischenschaltung eines Schwinghebels und die beiden außenliegenden Ventile direkt über Tassenstößel betätigt werden.US Pat. No. 4,637,356 discloses a valve drive with three intake valves actuated by a camshaft, the middle valves of which are actuated directly via bucket tappets with the interposition of a rocker arm and the two external valves.

Aus DE-36 00 408 C2 ist ein Zylinderkopf mit drei Einlaßventilen bekannt, bei dem jedem Einlaßkanal ein eigenes, mit einer Drosselklappe und einem Einspritzventil versehenes Saugrohr zugeordnet ist. Zur Erzeugung einer Drallbewegung der Ladung wird in einem ersten Betriebsbereich nur ein einziges, außenliegendes Einlaßventil betätigt. Bei steigender Drehzahl werden nacheinander die Drosselklappen und Einspritzventile des zweiten und dritten Einlaßventiles betätigt.From DE-36 00 408 C2 a cylinder head with three intake valves is known, in which each intake port is assigned its own intake manifold provided with a throttle valve and an injection valve. To generate a swirl movement of the load, only a single, external inlet valve is actuated in a first operating range. With increasing speed, the throttle valves and injectors of the second and third intake valves are actuated in succession.

Der Erfindung liegt die Aufgabe zugrunde, einen Zylinderkopf für eine Brennkraftmaschine mit verbesserten Leistungs- und Drehmomentwerten zu schaffen.The invention has for its object to provide a cylinder head for an internal combustion engine with improved power and torque values.

Die Lösung dieser Aufgabe gelingt mit den Merkmalen des Patentanspruches 1.Vorteilhafte Ausgestaltungen sind in den Unteransprüchen genannt.This object is achieved with the features of claim 1. Advantageous refinements are mentioned in the subclaims.

Wenn in einem gattungsgemäßen Zylinderkopf ein in Umfangsrichtung eines jeden Zylinders erstes Gaswechselventil unter Zwischenschaltung eines Betätigungshebels angeordnet permanent und die übrigen Ventile dieser Gruppe zeitweise betätigt werden, so ist dieser Zylinderkopf bezüglich des Ladungswechsel optimiert und liefert eine erhöhte Leistungs- und Drehmomentausbeute.
Das permanent betriebene Ventil ermöglicht durch den Verzicht auf einen raumgreifenden Tassenstößel eine platzsparende Anordnung am Rande eines Brennraumes. Die dadurch erzielte tangentiale Einströmung verursacht eine gezielte, rotierende Ladungsbewegung ("Swirl"). Die radiale Anordnung dieses Ventiles ermöglicht es, das oder die weiteren Ventile der ersten Gruppe vergleichsweise groß zu gestalten und somit einen optimalen Gasdurchsatz für hohe Leistungen zu erzielen. Da dieser erhöhte Gasdurchsatz nur bei hohen Lasten erforderlich ist, sind die weiteren Ventile mittels Schaltmechanismen zu- bzw. abschaltbar.
Diese Mechanismen können in vielfältiger Weise ausgestaltet sein, so z.B. als in einen hydraulischen Stößel integrierte Schaltvorrichtung gemäß DE-40 27 630 C oder als die entsprechenden Nocken an die Nockenwelle an- bzw. abkoppelnde Einrichtungen gemäß DE-41 00 763 A und werden daher nicht näher erläutert.If in a generic cylinder head a gas exchange valve arranged in the circumferential direction of each cylinder is arranged permanently with the interposition of an actuating lever and the other valves of this group are actuated temporarily, this cylinder head is optimized with regard to the gas exchange and delivers an increased power and torque yield.
By dispensing with a large tappet, the permanently operated valve enables a space-saving arrangement on the edge of a combustion chamber. The thereby achieved Tangential inflow causes a targeted, rotating charge movement ("Swirl"). The radial arrangement of this valve makes it possible to make the one or more valves of the first group comparatively large and thus to achieve an optimal gas throughput for high outputs. Since this increased gas throughput is only required at high loads, the other valves can be switched on and off using switching mechanisms.
These mechanisms can be designed in a variety of ways, for example as a switching device integrated in a hydraulic tappet according to DE-40 27 630 C or as the corresponding cams coupling or uncoupling devices according to DE-41 00 763 A and are therefore not explained in more detail.

Zur weiteren Optimierung ist dem permanent betriebenen, als Einlaßventil ausgebildeten Gaswechselventil ein erstes separates Saugrohr zugeordnet und den weiteren Ventilen dieser Grupppe ein weiteres. Die Saugrohre können somit in ihrer Geometrie an die unterschiedlichen Anforderungen eines Niedriglast- bzw. eines Hochlastbetriebes angepaßt werden.For further optimization, the permanently operated gas exchange valve, which is designed as an inlet valve, is assigned a first separate intake manifold and another valve of this group. The geometry of the intake manifolds can thus be adapted to the different requirements of a low-load or a high-load operation.

Wird der Zylinderkopf an einer fremdgezündeten Brennkraftmaschine betrieben, so sind diesen Saugrohren entsprechende Vorrichtungen zur Zufuhr und Kraftstoff zugeordnet und ein zentral im Zylinderkopf oberhalb jedes Zylinders angeordneter Schacht dient der Aufnahme einer Zündkerze.
An einer selbstzündenden Brennkraftmaschine nimmt dieser Schacht stattdessen die Vorrichtung zur Zufuhr von Kraftstoff auf.If the cylinder head is operated on a spark-ignited internal combustion engine, corresponding intake and fuel devices are assigned to these intake manifolds, and a shaft arranged centrally in the cylinder head above each cylinder serves to receive a spark plug.
On a self-igniting internal combustion engine, this shaft instead accommodates the device for supplying fuel.

Weist die erste Gruppe von Gaswechselventilen z.B. drei Einlaßventile auf, so kann die Brennkraftmaschine bei niedrigen Lasten kraftstoffsparend mit nur einem, im Durchmesser vergleichsweise kleinen, ersten Einlaßventil betrieben werden. Ein Auslaßventil der zweiten Gruppe kann dabei ebenso mit einem Schaltmechanismus versehen sein. Die Brennkraftmaschine kann dann als Zweiventilmotor betrieben werden, wobei nur eine geringe Antriebsleistung für den Ventiltrieb erforderlich ist.
Bei steigenden Lasten werden dann zeitgleich oder nacheinander die beiden weiteren Einlaßventile und das zweite Auslaßventil zugeschaltet. Der Gasdurchsatz erfolgt dann im wesentlichen über die vergleichsweise groß dimensionierten weiteren Ventile, so daß die Brennkraftmaschine dann als leistungsoptimierter 4-Ventilmotor betrachtet werden kann.If the first group of gas exchange valves has, for example, three inlet valves, then the internal combustion engine can be operated at low loads in a fuel-saving manner with only one first inlet valve, which is comparatively small in diameter. An outlet valve of the second group can also be provided with a switching mechanism. The internal combustion engine can then be operated as a two-valve engine be, whereby only a low drive power is required for the valve train.
With increasing loads, the two further inlet valves and the second outlet valve are then switched on simultaneously or in succession. The gas throughput then takes place essentially via the comparatively large additional valves, so that the internal combustion engine can then be regarded as a performance-optimized 4-valve engine.

In weiterer vorteilhafter Ausgestaltung sind die Winkellagen der Mittellängsachsen der Gaswechselventile so gewählt, daß sich ein möglichst glattes Brennraumdach ohne Zerklüftungen ergibt. Hierdurch wird eine klopfende Verbrennung weitestgehend vermieden und die Klopfgrenze ist in Richtung auf höhere Leistungsausbeute verschoben.In a further advantageous embodiment, the angular positions of the central longitudinal axes of the gas exchange valves are selected so that the combustion chamber roof is as smooth as possible without fissures. Knocking combustion is thereby largely avoided and the knock limit is shifted in the direction of higher power yield.

Die Erfindung wird anhand einer Zeichnung nachfolgend beispielhaft näher erläutert:The invention is explained in more detail below by way of example using a drawing:

Es zeigen:

Fig. 1
eine Draufsicht auf einen Zylinderkopf einer Brennkraftmaschine,
Fig. 2
einen Schnitt entlang der Linie II-II gemäß Fig.1,
Fig. 3
einen Schnitt entlang der Linie III-III gemäß Fig.1,
Fig. 4
einen Schnitt entlang der Linie IV-IV gemäß Fig.1 und
Fig. 5
eine Ansicht aus Richtung des Pfeiles X gemäß Fig.2.
Show it:
Fig. 1
a plan view of a cylinder head of an internal combustion engine,
Fig. 2
2 shows a section along the line II-II according to FIG. 1,
Fig. 3
2 shows a section along the line III-III according to FIG. 1,
Fig. 4
a section along the line IV-IV of Figure 1 and
Fig. 5
a view from the direction of arrow X according to Fig.2.

Eine mehrzylindrige Brennkraftmaschine weist einen mit Gaswechselkanälen versehenen Zylinderkopf 1 mit einem eingesetzten Lagerrahmen 2 auf. Einerseits einer Längsmittelebene L des Zylinderkopfes 1 sind die Kanäle als Einlaßkanäle 3, 4, 5 ausgebildet, welche sich von mit Einspritzventilen 6 versehenen und als Saugrohre 7 ausgebildeten Rohrstutzen ausgehend bis zu einem Brennraum 8 erstrecken.A multi-cylinder internal combustion engine has a cylinder head 1 provided with gas exchange channels with an inserted bearing frame 2. On the one hand, a longitudinal center plane L of the cylinder head 1, the ducts are designed as inlet ducts 3, 4, 5, which extend from pipe connections provided with injection valves 6 and designed as intake manifolds 7 to a combustion chamber 8.

Andererseits der Ebene L erstrecken sich vom Brennraum 8 ausgehend Auslaßkanäle 9, 10 zu einer Wand 11 des Zylinderkopfes 1.On the other hand, the level L extends from the combustion chamber 8, exhaust channels 9, 10 to a wall 11 of the cylinder head 1.

Die Einlaß- bzw. Auslaßkanäle 3, 4, 5 bzw. 9, 10 werden von einer ersten bzw. zweiten Gruppe von Gaswechselventilen beherrscht, welche als Einlaß- bzw. Auslaßventile 12, 13, 14 bzw. 15, 16 ausgebildet sind. Die Einlaßventile 12, 13 und 14 sind entlang einer Umfangsrichtung jedes Zylinders angeordnet.The inlet and outlet channels 3, 4, 5 and 9, 10 are dominated by a first and second group of gas exchange valves, which are designed as inlet and outlet valves 12, 13, 14 and 15, 16, respectively. The intake valves 12, 13 and 14 are arranged along a circumferential direction of each cylinder.

Der Lagerrahmen 2 weist Lager 17, 18 für nur schematisch gezeigte Nockenwellen auf, wobei in ersten Lagern 17 eine als Einlaßnockenwelle 19 ausgebildete erste Nockenwelle und in den zweiten Lagern 18 eine dementsprechende Auslaßnockenwelle 20 gelagert ist. Das erste Einlaßventil 12 wird unter Zwischenschaltung eines mit einer Rolle 21 versehenen, als Schwinghebel 22 ausgebildeten Betätigungshebels von der Einlaßnockenwelle 19 bewegt, welche das zweite und dritte Einlaßventil 13, 14 mittels Tassenstößeln 23 öffnet bzw. schließt. Die Tassenstößel 23 sind dabei in Aufnahmen 24 des Lagerrahmens 2 gleitverschieblich gelagert. Die beiden Auslaßventile 15 und 16 werden ebenfalls unter Vermittlung von Tassenstößeln 23 direkt von der Auslaßnockenwelle 20 betätigt.The bearing frame 2 has bearings 17, 18 for only schematically shown camshafts, a first camshaft designed as an intake camshaft 19 being mounted in first bearings 17 and a corresponding exhaust camshaft 20 being mounted in the second bearings 18. The first inlet valve 12 is moved with the interposition of an actuating lever provided with a roller 21 and designed as a rocking lever 22 by the inlet camshaft 19, which opens and closes the second and third inlet valves 13, 14 by means of bucket tappets 23. The tappets 23 are slidably mounted in receptacles 24 of the bearing frame 2. The two exhaust valves 15 and 16 are also actuated directly by the exhaust camshaft 20 by means of bucket tappets 23.

Das erste Einlaßventil 12 wird in allen Betriebspunkten der Brennkraftmaschine permanent betätigt und gewährleistet eine tangentiale Einströmung in den Brennraum 8, wodurch eine gezielte Ladungsbewegung erzielt wird.
Die weiteren Einlaßventile 13, 14 und ein Auslaßventil 16 sind mittels in den Tassenstößeln 23 integrierter, nicht gezeigter hydraulischer Schaltmechanismen wahlweise an die Nockenwellen 19, 20 koppelbar.
Bei niedriger Last der Brennkraftmaschine sind die Einlaßventile 13, 14 und das zweite Auslaßventil 16 stillgelegt. Mit steigender Last werden dann nacheinander die zunächst abgeschalteten Ventile zugeschaltet.The first inlet valve 12 is permanently actuated in all operating points of the internal combustion engine and ensures a tangential inflow into the combustion chamber 8, as a result of which a targeted charge movement is achieved.
The further inlet valves 13, 14 and an outlet valve 16 can optionally be coupled to the camshafts 19, 20 by means of hydraulic switching mechanisms (not shown) integrated in the tappets 23.
At low engine load, the intake valves 13, 14 and the second exhaust valve 16 are shut down. With increasing load, the valves that were initially switched off are then switched on in succession.

Alle Gaswechselventile sind als Tellerventile ausgebildet, wobei der Durchmesser D des ersten Einlaßventiles 12 geringer bemessen ist als der der übrigen Ventile.All gas exchange valves are designed as poppet valves, the diameter D of the first inlet valve 12 being smaller than that of the other valves.

Der dem ersten Einlaßventil 12 zugeordnete Einlaßkanal 3 ist mit einem ersten Saugrohr 7 verbunden, welches ein Einspritzventil 6 aufweist. Die weiteren Einlaßkanäle 4 und 5 sind gemeinsam an ein zweites Saugrohr 7 angeschlossen, welches ebenfalls ein Einspritzventil 6 aufweist. Die Saugrohre 7 sind dabei lösbar an einer Außenwandung 26 des Zylinderkopfes 1 gehalten.The inlet duct 3 assigned to the first inlet valve 12 is connected to a first intake manifold 7, which has an injection valve 6. The further inlet channels 4 and 5 are jointly connected to a second intake pipe 7, which also has an injection valve 6. The intake pipes 7 are detachably held on an outer wall 26 of the cylinder head 1.

Zentral im Zylinderkopf 1 bzw. Lagerrahmen 2 ist oberhalb jedes Zylinders ein Schacht 30 ausgebildet, welcher mit einer Öffnung 31 in den Brennraum 8 mündet und von der Längsmittelebene L geschnitten wird. In diese Öffnung 31 ist als Zündvorrichtung eine Zündkerze 32 eingesetzt.A shaft 30 is formed centrally in the cylinder head 1 or bearing frame 2 above each cylinder, which opens into the combustion chamber 8 with an opening 31 and is cut by the longitudinal center plane L. A spark plug 32 is inserted into this opening 31 as an ignition device.

Alle Gaswechselventile bewegen sich entlang ihrer Mittellängsachsen, wobei die Einlaßventile 12, 13, 14 derart angeordnet sind, daß deren Mittellängsachsen 33, 34, 35 ein Brennraumdach 36 in der Weise schneiden, daß die dabei entstehenden Schnittpunkte 37 einen jeweils voneinander verschiedenen Abstand A1, A2 und A3 zu der Mittellängsebene L aufweisen.
Die Mittellängsachsen 33 und 34 des ersten und zweiten Einlaßventiles 12 und 13 verlaufen parallel zueinander, wobei Mittellängsachse 33 einen Winkel 38 mit der Mittellängsebene L einschließt, welcher kleiner ist als der korrespondierende Winkel 39 der Mittellängsachse 35 des dritten Einlaßventiles 14.
Den Auslaßventilen 15 und 16 zugeordnete Mittellängsachsen 40 sowie die der Einlaßventile 13 und 14 schneiden jeweils Längsachsen 41 der Nockenwellen 19, 20.All gas exchange valves move along their central longitudinal axes, the inlet valves 12, 13, 14 being arranged in such a way that their central longitudinal axes 33, 34, 35 intersect a combustion chamber roof 36 in such a way that the intersection points 37 which arise in this case have a different distance A1, A2 and A3 to the central longitudinal plane L.
The central longitudinal axes 33 and 34 of the first and second inlet valves 12 and 13 run parallel to one another, the central longitudinal axis 33 including an angle 38 with the central longitudinal plane L, which is smaller than the corresponding angle 39 of the central longitudinal axis 35 of the third inlet valve 14.
The central longitudinal axes 40 assigned to the exhaust valves 15 and 16 and those of the intake valves 13 and 14 each cut longitudinal axes 41 of the camshafts 19, 20.

Der Schwinghebel 22 weist ein hydraulisches Ventilspielausgleichselement 42 auf, welches über Bohrungen 43 mit Drucköl versorgt wird. Dieser Hebel 22 ist drehbar auf einer Achse 44 gelagert, welcher einerseits in einem Lagerarm 45 des Rahmens 2 gehalten ist. In diesem Arm 45 verläuft eine Zufuhrbohrung 46 zur Versorgung des Ausgleichselementes 42 und zur Schmierung des Schwinghebels 22.The rocker arm 22 has a hydraulic valve clearance compensation element 42, which is supplied with pressure oil via bores 43. This lever 22 is rotatably mounted on an axis 44, which is on the one hand in a bearing arm 45 of the frame 2 is held. A feed bore 46 runs in this arm 45 for supplying the compensating element 42 and for lubricating the rocker arm 22.

Claims (15)

Zylinderkopf für eine Brennkraftmaschine, mit einer auf einer Seite einer Mittellängsebene des Zylinderkopfes angeordneten ersten Gruppe und einer auf der anderen Seite dieser Ebene angeordneten zweiten Gruppe von Gaswechselventilen,
mit diesen Gruppen zugeordneter erster und zweiter Nockenwelle, wobei mindestens ein Gaswechselventil der ersten Gruppe unter Zwischenschaltung eines Betätigungshebels von der ersten Nockenwelle betätigt wird und zumindest die erste Gruppe entlang einer Umfangsrichtung eines Zylinders der Brennkraftmaschine angeordnet ist, dadurch gekennzeichnet, daß der Betätigungshebel einem in der Umfangsrichtung ersten Gaswechselventil zugeordnet ist, welches permanent von der ersten Nockenwelle betätigt ist und daß das/die restlichen Ventile dieser Gruppe zeitweise betätigbar ist/sind.Cylinder head for an internal combustion engine, with a first group arranged on one side of a central longitudinal plane of the cylinder head and a second group of gas exchange valves arranged on the other side of this plane,
first and second camshafts assigned to these groups, at least one gas exchange valve of the first group being actuated by the first camshaft with the interposition of an actuating lever and at least the first group being arranged along a circumferential direction of a cylinder of the internal combustion engine, characterized in that the actuating lever engages one in the Associated with the circumferential direction is the first gas exchange valve, which is permanently actuated by the first camshaft and that the remaining valve (s) in this group can / are temporarily operable. Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß jedes Gaswechselventil der ersten Gruppe in einem eigenen Gaswechselkanal des Zylinderkopfes (1) angeordnet ist und daß an einer Außenwandung (26) des Zylinderkopfes (1) zwei den Kanälen zugeordnete Rohrstutzen angeordnet sind, wobei ein erster Rohrstutzen ausschließlich mit einem Gaswechselkanal des ersten Gaswechselventiles verbunden ist.Cylinder head according to claim 1, characterized in that each gas exchange valve of the first group is arranged in its own gas exchange channel of the cylinder head (1) and that two pipe sockets assigned to the channels are arranged on an outer wall (26) of the cylinder head (1), a first pipe socket is exclusively connected to a gas exchange channel of the first gas exchange valve. Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß die erste Gruppe aus Einlaßventilen (12, 13, 14) gebildet ist, deren Gaswechselkanäle als Einlaßkanäle (3, 4, 5) ausgebildet sind, wobei der das erste Einlaßventil (12) aufweisende erste Einlaßkanal (3) mit einem als ersten Saugrohr (7) ausgebildeten Rohrstutzen verbunden ist.Cylinder head according to Claim 1, characterized in that the first group is formed from intake valves (12, 13, 14), the gas exchange channels of which are designed as intake channels (3, 4, 5), the first intake valve (12) having the first intake valve (12) 3) is connected to a pipe socket designed as a first suction pipe (7). Zylinderkopf nach Anspruch 3, dadurch gekennzeichnet, daß die erste Gruppe ein zweites und drittes Einlaßventil (13 und 14) aufweist, deren zweiter und dritter Einlaßkanal (4 und 5) mit einem als zweiten Saugrohr (7) ausgebildeten Rohrstutzen verbunden ist.Cylinder head according to claim 3, characterized in that the first group has a second and third intake valve (13 and 14), the second and third intake ports (4 and 5) is connected to a pipe socket designed as a second suction pipe (7). Zylinderkopf nach Anspruch 3, dadurch gekennzeichnet, daß benachbart der in einen Brennraum (8) mündenden Einlaßkanäle (3, 4, 5) eine diesen Brennraum (8) mit einem zentral im Zylinderkopf (1) angeordneten und von der Mittellängsebene (L) geschnittenen Schacht (30) verbindende Öffnung (31) angeordnet ist.Cylinder head according to claim 3, characterized in that adjacent to the inlet ducts (3, 4, 5) opening into a combustion chamber (8) is a combustion chamber (8) with a shaft arranged centrally in the cylinder head (1) and cut from the central longitudinal plane (L) (30) connecting opening (31) is arranged. Zylinderkopf nach Anspruch 5, dadurch gekennzeichnet, daß in die Öffnung (31) eine Zündvorrichtung eingesetzt ist und die Saugrohre (7) mit einer Vorrichtung zur Zufuhr von Kraftstoff versehen sind.Cylinder head according to claim 5, characterized in that an ignition device is inserted into the opening (31) and the intake pipes (7) are provided with a device for supplying fuel. Zylinderkopf nach Anspruch 5, dadurch gekennzeichnet, daß in die Öffnung (31) eine Vorrichtung zur Zufuhr von Kraftstoff eingesetzt ist.Cylinder head according to claim 5, characterized in that a device for supplying fuel is inserted into the opening (31). Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß die restlichen Ventile der ersten Gruppe zeitgleich zu- bzw. abgeschaltet werden.Cylinder head according to claim 1, characterized in that the remaining valves of the first group are switched on or off at the same time. Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß die restlichen Ventile der ersten Gruppe zeitversetzt zueinander zu- bzw. abgeschaltet werden.Cylinder head according to claim 1, characterized in that the remaining valves of the first group are switched on and off at different times. Zylinderkopf nach Anspruch 8 oder 9, dadurch gekennzeichnet, daß mindestens ein als erstes Auslaßventil (15) ausgebildetes Gaswechselventil der zweiten Gruppe permanent von der zweiten Nockenwelle betätigt ist.Cylinder head according to Claim 8 or 9, characterized in that at least one gas exchange valve of the second group, which is designed as a first exhaust valve (15), is permanently actuated by the second camshaft. Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß alle weiteren Gaswechselventile von den Nockenwellen unter Zwischenschaltung von Tassenstößeln (23) betätigt werden.Cylinder head according to claim 1, characterized in that all further gas exchange valves are actuated by the camshafts with the interposition of bucket tappets (23). Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß alle Gaswechselventile als Tellerventile ausgebildet sind, wobei der Durchmesser (D) des Tellers des ersten Ventiles geringer ist als der des/der übrigen Ventile dieser Gruppe.Cylinder head according to claim 1, characterized in that all gas exchange valves are designed as poppet valves, wherein the diameter (D) of the plate of the first valve is smaller than that of the other valves in this group. Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß die Mittellängsachsen (33, 34, 35) der Ventile der ersten Gruppe ein Brennraumdach (36) derart schneiden, daß die entstehenden Schnittpunkte (37) alle auf der einen Seite der Mittellängsebene (L) liegen und einen jeweils voneinander verschiedenen Abstand (A1, A2, A3) zu dieser Ebene (L) aufweisen.Cylinder head according to claim 1 , characterized in that the central longitudinal axes (33, 34, 35) of the valves of the first group intersect a combustion chamber roof (36) such that the intersection points (37) which arise are all on one side of the central longitudinal plane (L) and have a different distance (A1, A2, A3) from this plane (L). Zylinderkopf nach Anspruch 13, dadurch gekennzeichnet, daß die Mittellängsachsen (33) des ersten Gaswechselventiles und eines in Umfangrichtung benachbarten Ventiles dieser Gruppe parallel zueinander verlaufend angeordnet sind.Cylinder head according to claim 13, characterized in that the central longitudinal axes (33) of the first gas exchange valve and a valve of this group which is adjacent in the circumferential direction are arranged parallel to one another. Zylinderkopf nach Anspruch 14, dadurch gekennzeichnet, daß die Mittellängsachse (33) des ersten Gaswechselventiles einen Winkel (38) mit der Mittellängsebene (L) einschließt, welcher kleiner ist als der korrespondierende Winkel (39) der Mittellängsachse (35) eines in Umfangsrichtung beabstandeten Ventiles dieser Gruppe.Cylinder head according to claim 14, characterized in that the central longitudinal axis (33) of the first gas exchange valve encloses an angle (38) with the central longitudinal plane (L) which is smaller than the corresponding angle (39) of the central longitudinal axis (35) of a circumferentially spaced valve this group.
EP94101746A 1993-03-09 1994-02-05 Cylinder head for an internal combustion engine Expired - Lifetime EP0615058B1 (en)

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DE4307368A DE4307368A1 (en) 1993-03-09 1993-03-09 Cylinder head for an internal combustion engine

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0699831A3 (en) * 1994-08-31 1996-05-15 Yamaha Motor Co Ltd Internal combustion engine and method for operating the same
US5758612A (en) * 1994-08-31 1998-06-02 Yamaha Hatsudoki Kabushiki Kaisha Valve actuating structure for multi-valve engine

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07197848A (en) * 1993-12-29 1995-08-01 Yamaha Motor Co Ltd Cylinder head of multicylinder engine
JPH08200023A (en) * 1995-01-24 1996-08-06 Toyota Motor Corp Cylinder head structure of internal combustion engine
DE19619183C1 (en) * 1996-05-11 1997-07-03 Porsche Ag Cylinder head arrangement for internal combustion engine
DE19828308A1 (en) * 1998-06-25 1999-12-30 Porsche Ag Cylinder head of an internal combustion engine
US7240663B2 (en) * 2004-03-19 2007-07-10 Ford Global Technologies, Llc Internal combustion engine shut-down for engine having adjustable valves
US7140355B2 (en) * 2004-03-19 2006-11-28 Ford Global Technologies, Llc Valve control to reduce modal frequencies that may cause vibration
US7128687B2 (en) * 2004-03-19 2006-10-31 Ford Global Technologies, Llc Electromechanically actuated valve control for an internal combustion engine
US7028650B2 (en) 2004-03-19 2006-04-18 Ford Global Technologies, Llc Electromechanical valve operating conditions by control method
US7383820B2 (en) * 2004-03-19 2008-06-10 Ford Global Technologies, Llc Electromechanical valve timing during a start
US7031821B2 (en) * 2004-03-19 2006-04-18 Ford Global Technologies, Llc Electromagnetic valve control in an internal combustion engine with an asymmetric exhaust system design
US7066121B2 (en) * 2004-03-19 2006-06-27 Ford Global Technologies, Llc Cylinder and valve mode control for an engine with valves that may be deactivated
US7055483B2 (en) * 2004-03-19 2006-06-06 Ford Global Technologies, Llc Quick starting engine with electromechanical valves
US7032545B2 (en) 2004-03-19 2006-04-25 Ford Global Technologies, Llc Multi-stroke cylinder operation in an internal combustion engine
US7128043B2 (en) * 2004-03-19 2006-10-31 Ford Global Technologies, Llc Electromechanically actuated valve control based on a vehicle electrical system
US7165391B2 (en) 2004-03-19 2007-01-23 Ford Global Technologies, Llc Method to reduce engine emissions for an engine capable of multi-stroke operation and having a catalyst
US7194993B2 (en) * 2004-03-19 2007-03-27 Ford Global Technologies, Llc Starting an engine with valves that may be deactivated
US7032581B2 (en) * 2004-03-19 2006-04-25 Ford Global Technologies, Llc Engine air-fuel control for an engine with valves that may be deactivated
US7017539B2 (en) * 2004-03-19 2006-03-28 Ford Global Technologies Llc Engine breathing in an engine with mechanical and electromechanical valves
US7072758B2 (en) 2004-03-19 2006-07-04 Ford Global Technologies, Llc Method of torque control for an engine with valves that may be deactivated
US7063062B2 (en) * 2004-03-19 2006-06-20 Ford Global Technologies, Llc Valve selection for an engine operating in a multi-stroke cylinder mode
US7021289B2 (en) * 2004-03-19 2006-04-04 Ford Global Technology, Llc Reducing engine emissions on an engine with electromechanical valves
US7555896B2 (en) * 2004-03-19 2009-07-07 Ford Global Technologies, Llc Cylinder deactivation for an internal combustion engine
US7107946B2 (en) * 2004-03-19 2006-09-19 Ford Global Technologies, Llc Electromechanically actuated valve control for an internal combustion engine
US7107947B2 (en) 2004-03-19 2006-09-19 Ford Global Technologies, Llc Multi-stroke cylinder operation in an internal combustion engine
US7559309B2 (en) * 2004-03-19 2009-07-14 Ford Global Technologies, Llc Method to start electromechanical valves on an internal combustion engine
US7079935B2 (en) * 2004-03-19 2006-07-18 Ford Global Technologies, Llc Valve control for an engine with electromechanically actuated valves
JP2013155647A (en) * 2012-01-27 2013-08-15 Suzuki Motor Corp Cam housing structure for three-dimensional cam

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2512493A1 (en) * 1981-09-10 1983-03-11 Honda Motor Co Ltd INTERNAL COMBUSTION ENGINE
US4617881A (en) * 1985-03-29 1986-10-21 Yamaha Hatsudoki Kabushiki Kaisha Actuating mechanism for multiple valve internal combustion engine
EP0213758A1 (en) * 1985-07-31 1987-03-11 Honda Giken Kogyo Kabushiki Kaisha Valve operating mechanism
EP0340834A2 (en) * 1988-05-05 1989-11-08 MOTORI MODERNI s.r.l. System of valves and related operating devices for internal combustion engines having high specific horsepower
EP0433728A1 (en) * 1989-11-29 1991-06-26 Yamaha Hatsudoki Kabushiki Kaisha Cylinder head and valve arrangement for a multi-valve internal combustion engine

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54153919A (en) * 1978-05-25 1979-12-04 Toyota Motor Corp Plural intake valve system internal combustion engine
JPS6149113A (en) * 1984-08-15 1986-03-11 Yamaha Motor Co Ltd Valve moving device of interval-combustion engine
US4667636A (en) * 1985-03-22 1987-05-26 Toyota Jidosha Kabushiki Kaisha Fuel injection type internal combustion engine
DE3600408A1 (en) * 1986-01-09 1987-07-16 Audi Ag Reciprocating piston internal combustion engine
JPH036801Y2 (en) * 1986-11-18 1991-02-20
JP2537263B2 (en) * 1988-04-12 1996-09-25 本田技研工業株式会社 Intake system for fuel injection engine
DE3815668A1 (en) * 1988-05-07 1989-11-16 Bosch Gmbh Robert VALVE CONTROL DEVICE WITH SOLENOID VALVE FOR INTERNAL COMBUSTION ENGINES
CA1331547C (en) * 1988-08-01 1994-08-23 Yukihiro Matsumoto Valve operating system for internal combustion engine
JPH04292526A (en) * 1991-03-20 1992-10-16 Honda Motor Co Ltd Four-cycle internal combustion engine
JPH05195736A (en) * 1992-01-20 1993-08-03 Mazda Motor Corp Valve driving device of engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2512493A1 (en) * 1981-09-10 1983-03-11 Honda Motor Co Ltd INTERNAL COMBUSTION ENGINE
US4617881A (en) * 1985-03-29 1986-10-21 Yamaha Hatsudoki Kabushiki Kaisha Actuating mechanism for multiple valve internal combustion engine
EP0213758A1 (en) * 1985-07-31 1987-03-11 Honda Giken Kogyo Kabushiki Kaisha Valve operating mechanism
EP0340834A2 (en) * 1988-05-05 1989-11-08 MOTORI MODERNI s.r.l. System of valves and related operating devices for internal combustion engines having high specific horsepower
EP0433728A1 (en) * 1989-11-29 1991-06-26 Yamaha Hatsudoki Kabushiki Kaisha Cylinder head and valve arrangement for a multi-valve internal combustion engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0699831A3 (en) * 1994-08-31 1996-05-15 Yamaha Motor Co Ltd Internal combustion engine and method for operating the same
US5758612A (en) * 1994-08-31 1998-06-02 Yamaha Hatsudoki Kabushiki Kaisha Valve actuating structure for multi-valve engine

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EP0615058B1 (en) 1997-10-15
DE59404294D1 (en) 1997-11-20
US5408958A (en) 1995-04-25
DE4307368A1 (en) 1994-09-15
KR940021915A (en) 1994-10-19
JPH06317112A (en) 1994-11-15

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