EP0900327A1 - Cylinder head for a multi-cylinder internal combustion engine - Google Patents

Cylinder head for a multi-cylinder internal combustion engine

Info

Publication number
EP0900327A1
EP0900327A1 EP97918132A EP97918132A EP0900327A1 EP 0900327 A1 EP0900327 A1 EP 0900327A1 EP 97918132 A EP97918132 A EP 97918132A EP 97918132 A EP97918132 A EP 97918132A EP 0900327 A1 EP0900327 A1 EP 0900327A1
Authority
EP
European Patent Office
Prior art keywords
valves
camshafts
cylinder head
cylinder
actuating elements
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP97918132A
Other languages
German (de)
French (fr)
Other versions
EP0900327B1 (en
Inventor
Salvador Ribes-Navarro
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.)
Audi AG
Original Assignee
Audi AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Audi AG filed Critical Audi AG
Publication of EP0900327A1 publication Critical patent/EP0900327A1/en
Application granted granted Critical
Publication of EP0900327B1 publication Critical patent/EP0900327B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis

Definitions

  • a cylinder head for a multi-cylinder internal combustion engine comprises at least two intake valves and two exhaust valves per cylinder, the valve disk centers of the intake valves and the valve disk centers of the exhaust valves not being arranged at the same distance from the perpendicular bisector of the cylinder head.
  • a generic cylinder head is known from WO 86/05237. This cylinder head is completely symmetrical. This results in a whole series of problems when accommodating the individual components in a confined space within the cylinder head.
  • the intake valves and the exhaust valves are controlled by two camshafts, a number of identically designed actuating elements are arranged between the valves and the cams of the camshafts and have the Cams of the camshafts assigned to valves have different base circle diameters. This ensures that the intake ports and the exhaust ports of the cylinder head on the receptacles for the Stud bolts of the cylinders, the bearings of the camshafts and the recesses for the injection nozzles can be passed.
  • the actuating elements being of identical design for all valves, there can be no confusion when equipping the cylinder head with the actuating elements.
  • the actuating elements associated with the inlet valves and the outlet valves are inclined to the camshafts to the same extent in order to achieve a uniform rolling or friction between the actuating element and the valve or the valve cap.
  • the object is achieved by the features of patent claim 2.
  • the inlet valves and the outlet valves are controlled by two camshafts, a number of identically designed actuating elements are arranged between the valves and the cams of the camshafts, and the actuating elements assigned to the valves are inclined to different degrees to the camshafts.
  • the bearings of the actuating levers are arranged at different heights.
  • the inlet and outlet valves as well as the actuating elements are arranged here in a manner that is almost contrary to symmetry.
  • the cams of the camshafts assigned to the valves have the same base circle diameters.
  • the two mentioned embodiments can also be combined with one another, so that the inlet valves and the outlet valves are controlled by two camshafts, that between the valves and the cams of the camshafts a number of identically designed actuating elements is arranged such that the cams assigned to the valves Camshafts have different base circle diameters and that the actuating elements assigned to the valves are inclined to different degrees to the camshafts. This then opens up a further degree of freedom, which allows even more extensive use of the space available in the cylinder head.
  • the valve springs of the inlet valves and the outlet valves, which counteract the actuating elements advantageously have different installation lengths depending on the position of the valve plate centers in the installed state.
  • valve springs which all have the same size and the same spring constant, act against the actuating elements with different forces depending on the installation length or compression.
  • the different forces are necessary since not only the valve plate centers of the valves but also the actuating elements are arranged at different distances from the perpendicular to the cylinder head or the camshafts, and different lever forces arise from the different distances of the actuating elements when they engage the cams of the camshafts surrender.
  • the actuating elements are preferably designed as rocker arms, the rocker arms being mounted on hydraulic support elements. This eliminates the need to store the actuating elements on separate shafts, so that there is a substantial saving in space.
  • the hydraulic support elements are particularly suitable for the arrangement of the actuating elements in differently inclined positions relative to the camshafts. The actuating elements can thus be arranged at different angles of inclination without any additional measures having to be taken.
  • Figure 1 is a plan view of the cylinder head according to the invention in a highly simplified schematic representation
  • FIG. 2 shows a section along the line If-Il * from FIG. 1, to illustrate the actuation of the two inlet valves according to the first embodiment of the invention
  • 3 shows another section along the line HI-HI 'from Figure 1 to illustrate the actuation of the two exhaust valves according to the first embodiment
  • Figure 4 shows a section along the line H-H 'of Figure 1, according to the second embodiment.
  • FIG. 5 shows a further section along the line III-II from FIG. 1 according to the second embodiment of the invention.
  • the cylinder head 1 has two intake valves 2 and two exhaust valves 3 per cylinder 4.
  • the valve plate centers 5 of the two intake valves 2 as well as the valve plate centers 5 'of the two exhaust valves 3 are arranged at different distances from the center perpendicular M of the cylinder head 1.
  • the valve stems 6 of the inlet valves 2 and the valve stems 6 'of the outlet valves 3 are at different distances from the axes of a first one and a second overhead camshaft 7, 7 '.
  • actuating elements 9 of identical design are arranged between the cams 8 of the camshafts 7, 7 'and the free ends of the valve stems 6, 6'. These actuation elements 9 are designed as simple rocker arms and are mounted on a hydraulic support element 10 with a hemispherical joint head 11.
  • the actuating elements 9 are brought to bear against the cams 8 of the camshafts 7, 7 'by means of a valve spring 12. As a result, the actuating elements 9, when acted upon by the cams 8, act counter to the force of the valve springs 12.
  • the intake valves 2 associated cam 8 of the camshaft 7, T differently sized Grund Vietnamese silk silk screen ⁇ diameter DG I, DQ2 on - ⁇ s can be clearly seen that there DQ I is greater AJS D ⁇ 32-
  • the various actuators 9 all have same position or inclination in the cylinder head 1.
  • the working area of the actuating elements 9 is defined by the respective base circle diameter DQ-), DQ2 unc * by the position of the intake valves 2.
  • the working area is the area with the cams 8 of the camshafts 7, 7 'is in contact.
  • the valve springs 12 used In order to be able to maintain approximately the same lever forces on the side of the support element 10 and on the side of the free end of the valve stem 6, 6 ', even with differently defined working areas of the actuating elements 9, the valve springs 12 used, all of which have the The same size and the same spring constant have different installation lengths Lpi, Lp2 when installed.
  • the installation length Lpi is chosen to be shorter than the installation length Lp2-
  • FIG. 3 a section along the line III-II I "through the two outlet valves 3 is shown in FIG. 3. It is clear from this illustration that the size relationships for the outlet valves 3 are exactly opposite Base circle diameter DQI smaller than the base circle diameter DG2- In addition, the installation length Lp-j of the one valve spring 12 is chosen to be greater than the installation length Lp2 of the other valve spring 12.
  • the base circle diameters DQ of the cams 8 of the camshafts 7, T are the same, while the actuating elements 9 assigned to the inlet valves 2 to the camshafts 7, T are smaller by the angle ⁇ are inclined differently.
  • the actuating elements 9 assigned to the inlet valves 2 to the camshafts 7, T are smaller by the angle ⁇ are inclined differently.
  • the rod ends 11 of the hydraulic support elements 10 are arranged somewhat offset in height. Such an offset in the height of the joint heads 11 is achieved in the case of the inclined support elements 10 shown by a displacement.
  • FIG. 5 shows a section through the outlet valves 3 according to the second embodiment of the invention.
  • the basic circle diameters DG of the cams 8 of the camshafts 7, T are of the same size and the actuating levers 9 are inclined differently by the angle ⁇ but in the opposite way.
  • one valve spring 12 is greater than the installation length Lp2 of the other valve spring 12.

Abstract

In order to make it particularly compact and easy to fit, the proposal is for a cylinder head (1) of a multi-cylinder internal combustion engine having at least two inlet valves (2) and two exhaust valves (3) per cylinder (4). The centre (5) of the head of the inlet of the inlet valves (2) and the centre (5') of the head of the exhaust valves (3) are not at the same distance from the mean perpendicular M of the cylinder head (1). In a first embodiment, the cylinder head is constructed in such a way that the inlet valves (2) and the outlet valves (3) are operated by two camshafts (7, 7'), there is a number of identical actuating components (9) between the valves (2, 3) and the cams (8) of the camshafts (7, 7'), and the cams (8) of the camshafts (7, 7) allocated to the valves (2, 3) have different basic circle diameters (DG1, DG2). In a second embodiment of the invention, the cylinder head (1) may also be designed in such a way that the inlet valves (2) and the exhaust valves (3) are controlled by two camshafts (7, 7'), there is a number of identical actuating components (9) between the valves (2, 3) and the cams (8) of the camshafts (7, 7'), and the actuating components (9) allocated to the valves (2, 3) are inclined in relation to the camshafts (7, 7') to widely differing degrees.

Description

B E S C H R E I B U N G DESCRIPTION
Zylinderkopf für eine mehrzylindrige BrennkraftmaschineCylinder head for a multi-cylinder internal combustion engine
Ein Zylinderkopf für eine mehrzylindrige Brennkraftmaschine umfaßt we¬ nigstens zwei Einlaßventile und zwei Auslaßventile pro Zylinder, wobei die Ventiltellermitten der Einlaßventile sowie die Ventiltellermitten der Ausla߬ ventile jeweils nicht in gleichem Abstand zur Mittelsenkrechten des Zylin¬ derkopfes angeordnet sind.A cylinder head for a multi-cylinder internal combustion engine comprises at least two intake valves and two exhaust valves per cylinder, the valve disk centers of the intake valves and the valve disk centers of the exhaust valves not being arranged at the same distance from the perpendicular bisector of the cylinder head.
Ein gattungsgemäßer Zylinderkopf ist aus der WO 86/05237 bekannt. Dieser Zylinderkopf ist völlig symmetrisch aufgebaut. Daraus ergeben sich eine ganze Reihe von Problemen bei der Unterbringung der einzelnen Bauteile auf engem Raum innerhalb des Zylinderkopfes.A generic cylinder head is known from WO 86/05237. This cylinder head is completely symmetrical. This results in a whole series of problems when accommodating the individual components in a confined space within the cylinder head.
Bedingt durch die ständig wachsenden Anforderungen an die Kompaktheit und die Montagefreundlichkeit der Zylinderköpfe von Brennkraftmaschi¬ nen ist es Aufgabe der vorliegenden Erfindung, einen Zylinderkopf zu konzipieren, der unter optimaler Ausnutzung des vorhandenen Baurau¬ mes eine verbesserte Unterbringung seiner diversen Komponenten er¬ laubt. Dabei soll gewährleistet sein, daß separat einzusetzende Teile auf¬ grund der Verwechslungsgefahr möglichst keine unterschiedlichen Geo¬ metrien aufweisen.Due to the constantly increasing demands on the compactness and the ease of installation of the cylinder heads of internal combustion engines, it is the object of the present invention to design a cylinder head which allows the various components to be better accommodated while making optimal use of the available space. It should be ensured that parts to be used separately do not have different geometries because of the risk of confusion.
Gelöst wird diese Aufgabe gemäß einer ersten Ausführungsform durch die Merkmale des Patentanspruchs 1. Demnach sind die Einlaßventile wie auch die Auslaßventile von zwei Nockenwellen gesteuert, sind zwischen den Ventilen und den Nocken der Nockenwellen eine Anzahl von iden¬ tisch ausgebildeten Betätigungselementen angeordnet und weisen die den Ventilen zugeordneten Nocken der Nockenwellen unterschiedliche Grundkreisdurchmesser auf. Dadurch wird erreicht, daß die Einlaßkanäle und die Auslaßkanäle des Zylinderkopfes an den Aufnahmen für die Stehbolzen der Zylinder, an den Lagerungen der Nockenwellen sowie an den Ausnehmungen für die Einspritzdüsen vorbeigeführt werden können. Darüber hinaus können bei dieser Ausführungsform aufgrund der für alle Ventile identisch ausgebildeten Betätigungselemente keine Verwechslun¬ gen bei der Bestückung des Zylinderkopfes mit den Betätigungselemen¬ ten auftreten. Zu beachten ist, daß bei dieser ersten Ausführungsform die den Einlaßventilen und den Auslaßventilen zugeordneten Betätigungs¬ elemente zu den Nockenwellen gleich stark geneigt sind, um eine gleichmäßige Abwälzung bzw. Reibung zwischen dem Betätigungsele¬ ment und dem Ventil bzw. den Ventilkäppchen zu erreichen.This object is achieved according to a first embodiment by the features of claim 1. Accordingly, the intake valves and the exhaust valves are controlled by two camshafts, a number of identically designed actuating elements are arranged between the valves and the cams of the camshafts and have the Cams of the camshafts assigned to valves have different base circle diameters. This ensures that the intake ports and the exhaust ports of the cylinder head on the receptacles for the Stud bolts of the cylinders, the bearings of the camshafts and the recesses for the injection nozzles can be passed. In addition, in this embodiment, due to the actuating elements being of identical design for all valves, there can be no confusion when equipping the cylinder head with the actuating elements. It should be noted that in this first embodiment, the actuating elements associated with the inlet valves and the outlet valves are inclined to the camshafts to the same extent in order to achieve a uniform rolling or friction between the actuating element and the valve or the valve cap.
Die Aufgabe wird gemäß einer zweiten Ausführungsform durch die Merk¬ male des Patentanspruchs 2 gelöst. Bei dieser Ausführungsform sind die Einlaßventile sowie die Auslaßventile von zwei Nockenwellen gesteuert, sind zwischen den Ventilen und den Nocken der Nockenwellen eine An¬ zahl von identisch ausgebildeten Betätigungselementen angeordnet, und sind die den Ventilen zugeordneten Betätigungselemente zu den Nockenwellen unterschiedlich stark geneigt. Dies geschieht, indem die Lagerungen der Betätigungshebel auf unterschiedlichen Höhen angeord¬ net sind. Damit ist eine ebenfalls kompakte Bauweise realisierbar, bei der die zwangsläufig symmetrisch angeordneten Befestigungselemente nicht mehr mit den Einlaß- und Auslaßkanälen sowie mit den Betätigungsele¬ menten kollidieren. Die Einlaß- und Auslaßventile sowie die Betätigungs¬ elemente sind hier quasi symmetriewidrig angeordnet. Zu beachten ist, daß bei dieser zweiten Ausführungsform die den Ventilen zugeordneten Nocken der Nockenwellen gleich große Grundkreisdurchmesser aufwei¬ sen.According to a second embodiment, the object is achieved by the features of patent claim 2. In this embodiment, the inlet valves and the outlet valves are controlled by two camshafts, a number of identically designed actuating elements are arranged between the valves and the cams of the camshafts, and the actuating elements assigned to the valves are inclined to different degrees to the camshafts. This is done in that the bearings of the actuating levers are arranged at different heights. This also makes it possible to implement a compact construction in which the inevitably symmetrically arranged fastening elements no longer collide with the inlet and outlet channels and with the actuating elements. The inlet and outlet valves as well as the actuating elements are arranged here in a manner that is almost contrary to symmetry. It should be noted that in this second embodiment, the cams of the camshafts assigned to the valves have the same base circle diameters.
Die beiden genannten Ausführungsformen können auch miteinander kombiniert werden, so daß die Einlaßventile sowie die Auslaßventile von zwei Nockenwellen gesteuert werden, daß zwischen den Ventilen und den Nocken der Nockenwellen eine Anzahl von identisch ausgebildeten Betä¬ tigungselementen angeordnet ist, daß die den Ventilen zugeordneten Nocken der Nockenwellen unterschiedlich große Grundkreisdurchmesser aufweisen und daß die den Ventilen zugeordneten Betätigungselemente zu den Nockenwellen unterschiedlich stark geneigt sind. Dadurch ist dann ein weiterer Freiheitsgrad erschlossen, was eine noch weitergehende Ausnutzung des im Zylinderkopf vorhandenen Bauraumes erlaubt. Vorteilhaft weisen die Ventilfedern der Einlaßventile und der Auslaßven¬ tile, welche den Betätigungselementen entgegenwirken, je nach Lage der Ventiltellermitten in eingebautem Zustand unterschiedliche Einbaulängen auf. Hierdurch wird erreicht, daß die Ventilfedern, die alle die gleiche Größe und die gleiche Federkonstante aufweisen, je nach Einbaulänge bzw. Kompression mit unterschiedlicher Kraft gegen die Betätigungsele¬ mente wirken. Die unterschiedlichen Kräfte sind erforderlich, da nicht nur die Ventiltellermitten der Ventile sondern auch die Betätigungselemente in verschiedenen Abständen zur Mittelsenkrechten des Zylinderkopfes bzw. den Nockenwellen angeordnet sind und sich aus den verschiedenen Ab¬ ständen der Betätigungselemente unterschiedliche Hebelkräfte bei der Anlage an den Nocken der Nockenwellen ergeben. Damit die verwende¬ ten Ventilfedern den daraus resultierenden unterschiedlichen Beanspru¬ chungen gerecht werden, ist es empfehlenswert verhältnismäßig weiche Ventilfedern zu wählen.The two mentioned embodiments can also be combined with one another, so that the inlet valves and the outlet valves are controlled by two camshafts, that between the valves and the cams of the camshafts a number of identically designed actuating elements is arranged such that the cams assigned to the valves Camshafts have different base circle diameters and that the actuating elements assigned to the valves are inclined to different degrees to the camshafts. This then opens up a further degree of freedom, which allows even more extensive use of the space available in the cylinder head. The valve springs of the inlet valves and the outlet valves, which counteract the actuating elements, advantageously have different installation lengths depending on the position of the valve plate centers in the installed state. It is hereby achieved that the valve springs, which all have the same size and the same spring constant, act against the actuating elements with different forces depending on the installation length or compression. The different forces are necessary since not only the valve plate centers of the valves but also the actuating elements are arranged at different distances from the perpendicular to the cylinder head or the camshafts, and different lever forces arise from the different distances of the actuating elements when they engage the cams of the camshafts surrender. In order that the valve springs used meet the resulting different demands, it is advisable to choose relatively soft valve springs.
Bevorzugt sind die Betätigungselemente als Schlepphebel ausgebildet, wobei die Schiepphebel auf hydraulischen Abstützelementen gelagert sind. Dadurch erübrigt sind die Lagerung der Betätigungselemente auf separaten Wellen, so daß eine wesentliche Platzersparnis gegeben ist. Zudem eignen sich die hydraulischen Abstützelemente aufgrund des Spielausgleichs in besonderer Weise für die Anordnung der Betätigungs¬ elemente in verschieden stark geneigten Stellungen relativ zu den Nockenwellen. Die Betätigungselemente können somit problemlos unter verschiedenen Neigungswinkeln angeordnet werden, ohne daß hierbei zusätzliche Maßnahmen getroffen werden müßten.The actuating elements are preferably designed as rocker arms, the rocker arms being mounted on hydraulic support elements. This eliminates the need to store the actuating elements on separate shafts, so that there is a substantial saving in space. In addition, due to the play compensation, the hydraulic support elements are particularly suitable for the arrangement of the actuating elements in differently inclined positions relative to the camshafts. The actuating elements can thus be arranged at different angles of inclination without any additional measures having to be taken.
Die vorliegende Erfindung wird unter Bezugnahme auf die nachfolgenden Zeichnungen näher erläutert. Es zeigen:The present invention is explained in more detail with reference to the following drawings. Show it:
Figur 1 eine Draufsicht des erfindungsgemäßen Zylinderkopfes in stark vereinfachter schematischer Darstellung;Figure 1 is a plan view of the cylinder head according to the invention in a highly simplified schematic representation;
Figur 2 einen Schnitt entlang der Linie If-Il* aus Figur 1 , zur Veran¬ schaulichung der Betätigung der beiden Einlaßventile gemäß der ersten Ausführungsform der Erfindung; Figur 3 einen anderen Schnitt entlang der Linie HI-HI' aus Figur 1 zur Veranschaulichung der Betätigung die beiden Auslaßventile gemäß der ersten Ausführungsform;FIG. 2 shows a section along the line If-Il * from FIG. 1, to illustrate the actuation of the two inlet valves according to the first embodiment of the invention; 3 shows another section along the line HI-HI 'from Figure 1 to illustrate the actuation of the two exhaust valves according to the first embodiment;
Figur 4 einen Schnitt entlang der Linie H-H' aus Figur 1 , gemäß der zweiten Ausführungsform; undFigure 4 shows a section along the line H-H 'of Figure 1, according to the second embodiment; and
Figur 5 einen weiteren Schnitt entlang der Linie III— f ll" aus Figur 1 ge¬ mäß der zweiten Ausführungsform der Erfindung.FIG. 5 shows a further section along the line III-II from FIG. 1 according to the second embodiment of the invention.
Wie in Figur 1 dargestellt ist, weist der erfindungsgemäße Zylinderkopf 1 jeweils zwei Einlaßventile 2 und zwei Auslaßventile 3 pro Zylinder 4 auf. Die Ventiltellermitten 5 der beiden Einlaßventile 2 wie auch die Ventiltel¬ lermitten 5' der beiden Auslaßventile 3 sind in verschiedenen Abständen zur Mittelsenkrechten M des Zylinderkopfes 1 angeordnet.As shown in FIG. 1, the cylinder head 1 according to the invention has two intake valves 2 and two exhaust valves 3 per cylinder 4. The valve plate centers 5 of the two intake valves 2 as well as the valve plate centers 5 'of the two exhaust valves 3 are arranged at different distances from the center perpendicular M of the cylinder head 1.
Da die Einlaßventile 2 und die Auslaßventile 3 im wesentlichen senkrecht stehen bzw. parallel zur den Achsen der Zylinder 4 orientiert sind, sind die Ventilschäfte 6 der Einlaßventile 2 und die Ventilschäfte 6' der Ausla߬ ventile 3, in verschiedenen Abständen zu den Achsen einer ersten und einer zweiten oben liegenden Nockenwelle 7, 7' angeordnet.Since the inlet valves 2 and the outlet valves 3 are substantially perpendicular or are oriented parallel to the axes of the cylinders 4, the valve stems 6 of the inlet valves 2 and the valve stems 6 'of the outlet valves 3 are at different distances from the axes of a first one and a second overhead camshaft 7, 7 '.
Wie aus den Figuren 2 bis 5 hervorgeht sind zwischen den Nocken 8 der Nockenwellen 7, 7' und den freien Enden der Ventilschäfte 6, 6' jeweils identisch ausgebildete Betätigungselemente 9 angeordnet. Diese Betäti¬ gungselemente 9 sind als einfache Schlepphebel ausgebildet und auf ei¬ nem hydraulischen Abstützelement 10 mit einem halbkugeligen Gelenk¬ kopf 11 gelagert.As can be seen from FIGS. 2 to 5, actuating elements 9 of identical design are arranged between the cams 8 of the camshafts 7, 7 'and the free ends of the valve stems 6, 6'. These actuation elements 9 are designed as simple rocker arms and are mounted on a hydraulic support element 10 with a hemispherical joint head 11.
Mittels einer Ventilfeder 12 werden die Betätigungselemente 9 zur Anlage gegen die Nocken 8 der Nockenwellen 7, 7' gebracht. Folglich wirken die Betätigungselemente 9 dann, wenn sie von den Nocken 8 beaufschlagt werden, entgegen der Kraft der Ventilfedern 12.The actuating elements 9 are brought to bear against the cams 8 of the camshafts 7, 7 'by means of a valve spring 12. As a result, the actuating elements 9, when acted upon by the cams 8, act counter to the force of the valve springs 12.
Entsprechend der in Figur 2 dargestellten ersten Ausführungsform der vorliegenden Erfindung weisen die den Einlaßventilen 2 zugeordneten Nocken 8 der Nockenwellen 7, T unterschiedlich große Grundkreisdurch¬ messer DG I , DQ2 auf- ^s ist deutlich erkennbar, daß dort DQ I größer ist ajs D<32- Somit haben die verschiedenen Betätigungselemente 9 alle die gleiche Stellung bzw. Neigung im Zylinderkopf 1. Durch den jeweiligen Grundkreisdurchmesser DQ-) , DQ2 unc* durch die Lage der Einlaßventile 2 definiert sich dabei der Arbeitsbereich der Betätigungselemente 9. Der Arbeitsbereich ist jener Bereich der mit den Nocken 8 der Nockenwellen 7, 7' in Kontakt steht.According to the embodiment illustrated in Figure 2 first embodiment of the present invention, the intake valves 2 associated cam 8 of the camshaft 7, T differently sized Grundkreisdurch¬ diameter DG I, DQ2 on - ^ s can be clearly seen that there DQ I is greater AJS D < 32- Thus, the various actuators 9 all have same position or inclination in the cylinder head 1. The working area of the actuating elements 9 is defined by the respective base circle diameter DQ-), DQ2 unc * by the position of the intake valves 2. The working area is the area with the cams 8 of the camshafts 7, 7 'is in contact.
Um selbst bei verschieden definierten Arbeitsbereichen der Betätigungs¬ elemente 9 annähernd gleiche Hebelkräfte auf der Seite des Abstützele¬ ments 10 und auf der Seite des freien Endes des Ventilschafts 6, 6' bei¬ behalten zu können, weisen die verwendeten Ventilfedern 12, welche alle die gleiche Größe und die gleiche Federkonstante haben, im eingebauten Zustand unterschiedliche Einbaulängen Lpi , Lp2 auf. In Figur 2 ist die Einbaulänge Lpi geringer gewählt als die Einbaulänge Lp2-In order to be able to maintain approximately the same lever forces on the side of the support element 10 and on the side of the free end of the valve stem 6, 6 ', even with differently defined working areas of the actuating elements 9, the valve springs 12 used, all of which have the The same size and the same spring constant have different installation lengths Lpi, Lp2 when installed. In Figure 2, the installation length Lpi is chosen to be shorter than the installation length Lp2-
Zum besseren Verständnis der Erfindung ist in Figur 3 noch ein Schnitt entlang der Linie III— II I" durch die beiden Auslaßventile 3 dargestellt. Aus dieser Darstellung wird klar, daß die Größenverhältnisse für die Ausla߬ ventile 3 gerade entgegengesetzt sind. Denn dort ist der Grundkreis¬ durchmesser DQI kleiner als der Grundkreisdurchmesser DG2- Außer¬ dem ist dort die Einbaulänge Lp-j der einen Ventilfeder 12 größer gewählt als die Einbaulänge Lp2 der anderen Ventilfeder 12.For a better understanding of the invention, a section along the line III-II I "through the two outlet valves 3 is shown in FIG. 3. It is clear from this illustration that the size relationships for the outlet valves 3 are exactly opposite Base circle diameter DQI smaller than the base circle diameter DG2- In addition, the installation length Lp-j of the one valve spring 12 is chosen to be greater than the installation length Lp2 of the other valve spring 12.
Gemäß der in Figur 4 dargestellten zweiten Ausführungsform der Erfin¬ dung sind die Grundkreisdurchmesser DQ der Nocken 8 der Nockenwel¬ len 7, T gleich, während die den Einlaßventilen 2 zugeordneten Betäti¬ gungselemente 9 zu den Nockenwellen 7, T um den Winkel α unter¬ schiedlich stark geneigt sind. Bei den unterschiedlichen Neigungswinkeln der Betätigungselemente 9 ergibt sich die gleiche Kinematik wie bei der ersten Ausführungsform, wenn die Gelenkköpfe 11 der hydraulischen Abstützelemente 10 in der Höhe etwas versetzt angeordnet sind. Ein sol¬ cher Versatz in der Höhe der Gelenkköpfe 11 wird bei den dargestellten schräg stehenden Abstützelementen 10 durch eine Verschiebung erreicht.According to the second embodiment of the invention shown in FIG. 4, the base circle diameters DQ of the cams 8 of the camshafts 7, T are the same, while the actuating elements 9 assigned to the inlet valves 2 to the camshafts 7, T are smaller by the angle α are inclined differently. With the different angles of inclination of the actuating elements 9, the same kinematics result as in the first embodiment if the rod ends 11 of the hydraulic support elements 10 are arranged somewhat offset in height. Such an offset in the height of the joint heads 11 is achieved in the case of the inclined support elements 10 shown by a displacement.
Auch bei dieser zweiten Ausführungsform weisen die Ventilfedern 12 der Einlaßventile 2 je nach Lage der Ventiltellermitten 5 in eingebautem Zu¬ stand unterschiedliche Einbaulängen Lp-j , Lp2 auf, damit auf beiden Sei¬ ten der Betätigungselemente 9 annähernd gleiche Hebelkräfte auftreten. In Figur 5 ist schließlich ein Schnitt durch die Auslaßventile 3 gemäß der zweiten Ausführungsform der Erfindung dargestellt. Dort sind die Grund¬ kreisdurchmesser DG der Nocken 8 der Nockenwellen 7, T gleich groß und sind die Betätigungshebel 9 um den Winkel α unterschiedlich stark aber in entgegengesetzter Weise geneigt. Außerdem ist dort ist die Ein¬ baulänge Lp-| der einen Ventilfeder 12 größer als die Einbaulänge Lp2 der anderen Ventilfeder 12.In this second embodiment, too, the valve springs 12 of the inlet valves 2 have different installation lengths Lp-j, Lp2, depending on the position of the valve plate centers 5 in the installed state, so that approximately the same lever forces occur on both sides of the actuating elements 9. Finally, FIG. 5 shows a section through the outlet valves 3 according to the second embodiment of the invention. There the basic circle diameters DG of the cams 8 of the camshafts 7, T are of the same size and the actuating levers 9 are inclined differently by the angle α but in the opposite way. There is also the installation length Lp- | one valve spring 12 is greater than the installation length Lp2 of the other valve spring 12.
Selbstverständlich können die beiden dargestellten Ausführungsformen auch gemeinsam in einem Zylinderkopf realisiert sein. Of course, the two illustrated embodiments can also be implemented together in one cylinder head.

Claims

PATENTANSPRÜCHE PATENT CLAIMS
1. Zylinderkopf für eine mehrzylindrige Brennkraftmaschine, mit1. Cylinder head for a multi-cylinder internal combustion engine, with
- wenigstens zwei Einlaßventilen (2) und zwei Auslaßventilen (3) pro Zylinder (4), wobei- At least two intake valves (2) and two exhaust valves (3) per cylinder (4), wherein
- die Ventiltellermitten (5) der Einlaßventile (2) sowie die Ventiltel¬ lermitten (5') der Auslaßventile (3) jeweils nicht in gleichem Ab¬ stand zur Mittelsenkrechten (M) des Zylinderkopfes (1) angeord¬ net sind,- The valve plate centers (5) of the inlet valves (2) and the valve plate centers (5 ') of the exhaust valves (3) are each not arranged at the same distance from the perpendicular (M) of the cylinder head (1).
dadurch gekennzeichnet, daßcharacterized in that
- die Einlaßventile (2) sowie die Auslaßventile (3) von zwei Nockenwellen (7, 7') gesteuert werden,- The intake valves (2) and the exhaust valves (3) are controlled by two camshafts (7, 7 '),
- zwischen den Ventilen (2, 3) und den Nocken (8) der Nockenwel¬ len (7, 7') eine Anzahl von identisch ausgebildeten Betätigungs¬ elementen (9) angeordnet ist, und- A number of identically designed actuating elements (9) is arranged between the valves (2, 3) and the cams (8) of the camshafts (7, 7 '), and
- die den Ventilen (2, 3) zugeordneten Nocken (8) der Nockenwel¬ len (7, 7') unterschiedlich große Grundkreisdurchmesser (DQI , DG2) aufweisen.- The cams (8) of the camshafts (7, 7 ') assigned to the valves (2, 3) have different base circle diameters (DQI, DG2).
2. Zyiinderkopf für eine mehrzylindrige Brennkraftmaschine, insbeson¬ dere nach Anspruch 1 , mit2. cylinder head for a multi-cylinder internal combustion engine, in particular according to claim 1, with
- wenigstens zwei Einlaßventilen (2) und zwei Auslaßventilen (3) pro Zylinder (4), wobei - die Ventiltellermitten (5) der Einlaßventile (2) sowie die Ventiltel¬ lermitten (5') der Auslaßventile (3) jeweils nicht in gleichem Ab¬ stand zur Mittelsenkrechten (M) des Zylinderkopfes (1) angeord¬ net sind,- At least two intake valves (2) and two exhaust valves (3) per cylinder (4), wherein - The valve plate centers (5) of the inlet valves (2) and the valve plate centers (5 ') of the exhaust valves (3) are each not arranged at the same distance from the perpendicular (M) of the cylinder head (1).
dadurch gekennzeichnet, daßcharacterized in that
- die Einlaßventile (2) sowie die Auslaßventile (3) von zwei Nockenwellen (7, 7') gesteuert werden,- The intake valves (2) and the exhaust valves (3) are controlled by two camshafts (7, 7 '),
- zwischen den Ventilen (2, 3) und den Nocken (8) der Nockenwel¬ len (7, 7') eine Anzahl von identisch ausgebildeten Betätigungs¬ elementen (9) angeordnet sind, und- A number of identically designed actuating elements (9) are arranged between the valves (2, 3) and the cams (8) of the camshafts (7, 7 '), and
- die den Ventilen (2, 3) zugeordneten Betätigungselemente (9) zu den Nockenwellen (7, 7') unterschiedlich stark geneigt sind.- The actuating elements (9) assigned to the valves (2, 3) are inclined to different degrees to the camshafts (7, 7 ').
3. Zylinderkopf nach einem der Ansprüche 1 oder 2, dadurch gekenn¬ zeichnet, daß die Betätigungselemente (9) jeweils entgegen der Kraft einer Ventilfeder (12) wirken, wobei die Ventilfedern (12) der Einlaßventile (2) sowie der Auslaßventile (3) je nach Lage der Ventil¬ tellermitten (5, 5') in eingebautem Zustand unterschiedliche Einbau¬ längen (Lp-| , Lp2) aufweisen.3. Cylinder head according to one of claims 1 or 2, characterized gekenn¬ characterized in that the actuating elements (9) each act against the force of a valve spring (12), the valve springs (12) of the intake valves (2) and the exhaust valves (3) have different installation lengths (Lp- |, Lp2) depending on the position of the valve disc centers (5, 5 ') in the installed state.
Zylinderkopf nach einem der Ansprüche 1 bis 3, dadurch gekenn¬ zeichnet, daß die Betätigungselemente (9) als Schlepphebel aus¬ gebildet sind.Cylinder head according to one of claims 1 to 3, characterized gekenn¬ characterized in that the actuating elements (9) are formed as a rocker arm.
5. Zylinderkopf nach Anspruch 4, dadurch gekennzeichnet, daß die Schlepphebel auf hydraulischen Abstützelementen (10) gelagert sind. 5. Cylinder head according to claim 4, characterized in that the rocker arms are mounted on hydraulic support elements (10).
EP97918132A 1996-05-22 1997-04-14 Cylinder head for a multi-cylinder internal combustion engine Expired - Lifetime EP0900327B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19620546A DE19620546A1 (en) 1996-05-22 1996-05-22 Cylinder head for a multi-cylinder internal combustion engine
DE19620546 1996-05-22
PCT/EP1997/001848 WO1997044576A1 (en) 1996-05-22 1997-04-14 Cylinder head for a multi-cylinder internal combustion engine

Publications (2)

Publication Number Publication Date
EP0900327A1 true EP0900327A1 (en) 1999-03-10
EP0900327B1 EP0900327B1 (en) 1999-11-17

Family

ID=7794974

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97918132A Expired - Lifetime EP0900327B1 (en) 1996-05-22 1997-04-14 Cylinder head for a multi-cylinder internal combustion engine

Country Status (4)

Country Link
EP (1) EP0900327B1 (en)
CN (1) CN1080822C (en)
DE (2) DE19620546A1 (en)
WO (1) WO1997044576A1 (en)

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Also Published As

Publication number Publication date
DE59700735D1 (en) 1999-12-23
DE19620546A1 (en) 1997-11-27
WO1997044576A1 (en) 1997-11-27
CN1080822C (en) 2002-03-13
EP0900327B1 (en) 1999-11-17
CN1219219A (en) 1999-06-09

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