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EP0615058B1 - Cylinder head for an internal combustion engine - Google Patents

Cylinder head for an internal combustion engine Download PDF

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Publication number
EP0615058B1
EP0615058B1 EP94101746A EP94101746A EP0615058B1 EP 0615058 B1 EP0615058 B1 EP 0615058B1 EP 94101746 A EP94101746 A EP 94101746A EP 94101746 A EP94101746 A EP 94101746A EP 0615058 B1 EP0615058 B1 EP 0615058B1
Authority
EP
European Patent Office
Prior art keywords
cylinder head
valves
group
valve
gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94101746A
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German (de)
French (fr)
Other versions
EP0615058A1 (en
Inventor
Willi Schultz
Joachim Dr. Esch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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Publication of EP0615058A1 publication Critical patent/EP0615058A1/en
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Classifications

    • 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.
  • a cylinder head for an internal combustion engine with two groups of gas exchange valves is known, which are arranged along the circumferential direction of a cylinder of the internal combustion engine and in each case on one side of the central longitudinal plane of the cylinder head. Both groups of gas exchange valves are actuated by a camshaft arranged in the cylinder head. This is done with the interposition of operating levers.
  • a cylinder head is known in which two gas exchange valves arranged on one side of the central longitudinal plane are acted upon by the camshaft via actuating levers, a first gas exchange valve being operated continuously and the other valve of this group being actuatable at times.
  • Another cylinder head is known from FR-A-25 12 493, in which two groups of gas exchange valves are actuated via rocker arms, one of the gas exchange valves being permanently operable by a camshaft and the other gas exchange valve belonging to this group temporarily.
  • 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 by means of bucket tappets, with the intermediary 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 resulting 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.
  • the other valves can be switched on and off using switching mechanisms.
  • These mechanisms can be designed in a variety of ways, e.g. 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 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. With increasing loads, the two further inlet channels are then switched on simultaneously or in succession. The gas throughput then takes place essentially via the comparatively large dimensioned further valves.
  • 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.
  • an outlet valve of the second group can also be provided with a switching mechanism.
  • the internal combustion engine can then be operated, for example, at low loads as a two-valve engine, with only a low drive power being required for the valve train. If, in addition to the further inlet valves, a second outlet valve is switched on with increasing loads, the gas exchange valve then essentially takes place via the comparatively large one dimensioned further intake valves and the two exhaust valves, so that the internal combustion engine can then be regarded as a performance-optimized four-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 controlled 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

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.

Aus der gattungsgemäßen EP-A-0 353 988 ist ein Zylinderkopf für eine Brennkraftmaschine mit zwei Gruppen von Gaswechselventilen bekannt, die entlang der Umfangsrichtung eines Zylinders der Brennkraftmaschine und jeweils auf einer Seite der Mittellängsebene des Zylinderkopfes angeordnet sind. Beide Gruppen von Gaswechselventilen werden jeweils von einer im Zylinderkopf angeordneten Nockenwelle betätigt. Dies erfolgt unter Zwischenschaltung von Betätigungshebeln.From the generic EP-A-0 353 988 a cylinder head for an internal combustion engine with two groups of gas exchange valves is known, which are arranged along the circumferential direction of a cylinder of the internal combustion engine and in each case on one side of the central longitudinal plane of the cylinder head. Both groups of gas exchange valves are actuated by a camshaft arranged in the cylinder head. This is done with the interposition of operating levers.

Aus der EP-A-0 213 758 ist ein Zylinderkopf bekannt, bei dem zwei auf einer Seite der Mittellängsebene angeordnete Gaswechselventile über Betätigungshebel von der Nockenwelle beaufschlagt werden, wobei ein erstes Gaswechselventil ständig betrieben wird und das andere Ventil dieser Gruppe zeitweise betätigbar ist.From EP-A-0 213 758 a cylinder head is known in which two gas exchange valves arranged on one side of the central longitudinal plane are acted upon by the camshaft via actuating levers, a first gas exchange valve being operated continuously and the other valve of this group being actuatable at times.

Aus der FR-A-25 12 493 ist ein weiterer Zylinderkopf bekannt, bei dem zwei Gruppen von Gaswechselventilen über Kipphebel betätigt werden, wobei eines der Gaswechselventile permanent von einer Nockenwelle und das andere zu dieser Gruppe gehörende Gaswechselventil zeitweise betätigbar ist.Another cylinder head is known from FR-A-25 12 493, in which two groups of gas exchange valves are actuated via rocker arms, one of the gas exchange valves being permanently operable by a camshaft and the other gas exchange valve belonging to this group temporarily.

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 by means of bucket tappets, with the intermediary 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. Durch die Anordnung von drei Einlaßventilen in der ersten Gruppe von Gaswechselventilen kann die Brennkraftmaschine bei niedrigen Lasten kraftstoffsparend mit nur einem, im Durchmesser vergleichsweise kleinen, ersten Einlaßventil betrieben werden. Bei steigenden Lasten werden dann zeitgleich oder nacheinander die beiden weiteren Einlaßkanäle zugeschaltet. Der Gasdurchsatz erfolgt dann im wesentlichen über die vergleichsweise groß dimensionierten weiteren Ventile.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 resulting 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, e.g. 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. By arranging three inlet valves in the first group of gas exchange valves, 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. With increasing loads, the two further inlet channels are then switched on simultaneously or in succession. The gas throughput then takes place essentially via the comparatively large dimensioned further valves.

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.

Zusätzlich kann dabei ein Auslaßventil der zweiten Gruppe ebenfalls mit einem Schaltmechanismus versehen sein. Die Brennkraftmaschine kann dann beispielsweise bei niedrigen Lasten als Zwei-Ventilmotor betrieben werden, wobei nur eine geringe Antriebsleistung für den Ventiltrieb erforderlich ist. Wird bei steigenden Lasten neben den weiteren Einlaßventilen ein zweites Auslaßventil zugeschaltet, erfolgt der Gaswechselventil dann im wesentlichen über die vergleichsweise groß dimensionierten weiteren Einlaßventile und die beiden Auslaßventile, so daß die Brennkraftmaschine dann als leistungsoptimierter Vier-Ventilmotor betrachtet werden kann.In addition, an outlet valve of the second group can also be provided with a switching mechanism. The internal combustion engine can then be operated, for example, at low loads as a two-valve engine, with only a low drive power being required for the valve train. If, in addition to the further inlet valves, a second outlet valve is switched on with increasing loads, the gas exchange valve then essentially takes place via the comparatively large one dimensioned further intake valves and the two exhaust valves, so that the internal combustion engine can then be regarded as a performance-optimized four-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 controlled 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 (14)

  1. A cylinder head for an internal-combustion engine, with a first group of gas-exchange valves arranged on one side of a median longitudinal plane of the cylinder head and a second group arranged on the other side of the said plane, with a first and second camshaft associated with the said groups, wherein at least one gas-exchange valve of the first group is actuated by the first camshaft with the interposition of an actuating lever and at least the first group is arranged along a peripheral direction of a cylinder of the internal-combustion engine, characterized in that the first group of gas-exchange valves is formed by three inlet valves (12, 13, 14), the actuating lever (22) is associated with the first inlet valve (12) in the peripheral direction, the said first inlet valve (12) being continuously actuated by the first camshaft (19), the remaining valves of this group are periodically actuable, and these valves and the gas-exchange valves (15, 16) of the second group are actuated with the interposition of flat tappets (23).
  2. A cylinder head according to Claim 1, characterized in that each gas-exchange valve of the first group is arranged in a separate gas-exchange duct of the cylinder head (1), and two pipe sockets associated with the ducts are arranged on an outer wall (26) of the cylinder head (1), wherein a first pipe socket is connected exclusively to the gas-exchange duct of the first gas-exchange valve.
  3. A cylinder head according to Claim 1, characterized in that the first group is formed by inlet valves (12, 13, 14), the gas-exchange ducts of which are constructed as inlet ducts (3, 4, 5), wherein the first inlet duct (3) comprising the first inlet valve (12) is connected to a pipe socket constructed as a first intake pipe (7).
  4. A cylinder head according to Claim 3, characterized in that the second and third inlet ducts (4 and 5) associated with the second and third inlet valves (13 and 14) are connected to a pipe socket constructed as a second intake pipe (7).
  5. A cylinder head according to Claim 3, characterized in that an opening (31) connecting a combustion chamber (8) to a cavity (30) arranged centrally in the cylinder head (1) and intersected by the median longitudinal plane (L) is arranged adjacent to the inlet ducts (3, 4, 5) opening into the said combustion chamber (8).
  6. A 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.
  7. A cylinder head according to Claim 5, characterized in that a device for supplying fuel is inserted into the opening (31).
  8. A cylinder head according to Claim 1, characterized in that the remaining valves of the first group are turned off and on in synchronism.
  9. A cylinder head according to Claim 1, characterized in that the remaining valves of the first group are turned off and on in a staggered manner.
  10. A cylinder head according to Claim 8 or 9, characterized in that at least one gas-exchange valve - constructed as a first exhaust valve (15) - of the second group is actuated continuously by the second camshaft.
  11. A cylinder head according to Claim 1, characterized in that all the gas-exchange valves are constructed as disc valves, the diameter (D) of the disc of the first valve being smaller than that of the remaining valve or valves of this group.
  12. A cylinder head according to Claim 1, characterized in that the median longitudinal axes (33, 34, 35) of the valves of the first group intersect a combustion-chamber head (36) in such a way that the resulting points of intersection (37) all lie on one side of the median longitudinal plane (L) and are at a respectively different distance (A1, A2, A3) from the said plane (L).
  13. A cylinder head according to Claim 12, characterized in that the median longitudinal axes (33) of the first gas-exchange valve and of a peripherally adjacent valve of this group are arranged so as to extend parallel to each other.
  14. A cylinder head according to Claim 13, characterized in that the median longitudinal axis (33) of the first gas-exchange valve forms an angle (38) with the median longitudinal plane (L), which is smaller than the corresponding angle (39) of the median longitudinal axis (35) of a peripherally spaced valve of this group.
EP94101746A 1993-03-09 1994-02-05 Cylinder head for an internal combustion engine Expired - Lifetime EP0615058B1 (en)

Applications Claiming Priority (2)

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DE4307368 1993-03-09
DE4307368A DE4307368A1 (en) 1993-03-09 1993-03-09 Cylinder head for an internal combustion engine

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EP0615058A1 EP0615058A1 (en) 1994-09-14
EP0615058B1 true EP0615058B1 (en) 1997-10-15

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EP (1) EP0615058B1 (en)
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DE4307368A1 (en) 1994-09-15
EP0615058A1 (en) 1994-09-14
US5408958A (en) 1995-04-25
KR940021915A (en) 1994-10-19
DE59404294D1 (en) 1997-11-20
JPH06317112A (en) 1994-11-15

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