EP0436779A1 - Cylinder head for internal-combustion engine - Google Patents

Cylinder head for internal-combustion engine Download PDF

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Publication number
EP0436779A1
EP0436779A1 EP90116952A EP90116952A EP0436779A1 EP 0436779 A1 EP0436779 A1 EP 0436779A1 EP 90116952 A EP90116952 A EP 90116952A EP 90116952 A EP90116952 A EP 90116952A EP 0436779 A1 EP0436779 A1 EP 0436779A1
Authority
EP
European Patent Office
Prior art keywords
cylinder head
head according
cylinder
carrier
receptacles
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
EP90116952A
Other languages
German (de)
French (fr)
Other versions
EP0436779B1 (en
Inventor
Manfred Dipl.-Ing. Batzill
Herbert Dipl.-Ing. Fh Ampferer
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
Original Assignee
Dr Ing HCF Porsche AG
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Publication date
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Publication of EP0436779A1 publication Critical patent/EP0436779A1/en
Application granted granted Critical
Publication of EP0436779B1 publication Critical patent/EP0436779B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/262—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with valve stems disposed radially from a centre which is substantially the centre of curvature of the upper wall surface of a combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/102—Lubrication of valve gear or auxiliaries of camshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/104—Lubrication of valve gear or auxiliaries of tappets
    • 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
    • F02F1/242—Arrangement of spark plugs or injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/006—Camshaft or pushrod housings
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • 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
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L2003/25—Valve configurations in relation to engine
    • F01L2003/256—Valve configurations in relation to engine configured other than perpendicular to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/02—Attachment or mounting of cylinder heads on cylinders
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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 
    • F02F1/02—Cylinders; Cylinder heads  having cooling means
    • F02F1/10—Cylinders; Cylinder heads  having cooling means for liquid cooling
    • F02F2001/104—Cylinders; Cylinder heads  having cooling means for liquid cooling using an open deck, i.e. the water jacket is open at the block top face
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
    • F02F2001/246—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis and orientated radially from the combustion chamber surface

Definitions

  • the invention relates to a cylinder head of an internal combustion engine according to the preamble of claim 1.
  • a camshaft bearing frame for an internal combustion engine with four valves per cylinder is known, which is screwed onto the cylinder head base housing as a separate part.
  • This bearing frame consists of a cast part with webs running transversely to the longitudinal direction between the cylinders and at the two ends of the cylinder head, and with two webs running parallel in the longitudinal direction, which rest on the lateral housing walls of the cylinder head.
  • Lower half-shells for the bearings of camshafts are formed in the transverse webs, the upper halves of which are formed by separate bearing covers which can be screwed onto the camshaft bearing frame.
  • This bearing frame enables the camshafts and their bearings to be pre-assembled separately.
  • DE 38 19 655 discloses a four-valve cylinder head for an internal combustion engine, in which the receptacles for the tappets are combined in pairs in the form of glasses.
  • This cylinder head has a complicated shape, which requires a sand casting process due to the many undercuts on the top side opposite the combustion chamber side. This process requires thorough and time-consuming cleaning of the top side after casting.
  • the resulting cast structure has a high degree of homogeneity and improved material properties compared to the known solutions. This significantly reduces the risk of cracks in the cylinder head housing.
  • the carrier can be produced independently of the cylinder head housing using the die casting process and can then be machined inexpensively.
  • Upper and lower girder sections each include parts of a central web and parts of several cross webs. To stiffen the crossbars, no separate, weight-increasing longitudinal webs are arranged in the carrier, rather this function is performed by struts running on both sides of the central web in the lower part of the carrier, which include tappet-guiding receptacles which are connected to one another by bridges.
  • Each receptacle is in turn supported by at least one support on the part of the central web running in the lower part of the carrier.
  • the tappet bearing, pair-cooperating receptacles of a cylinder are connected to one another via a bridge designed as a rib, while the bridge between receptacles belonging to adjacent cylinders as Bearing lower parts of bearings for two camshafts is formed. This creates a lightweight, stiff carrier, the struts of which contribute to stiffening the carrier and act as a bearing for cup tappets.
  • the pairs of cooperating receptacles of a cylinder are connected via a bridge designed as a bearing lower part of a bearing of a camshaft, the bridge between receptacles belonging to adjacent cylinders being connected via a bridge designed as a rib.
  • the central web extends in a ring shape above each cylinder to form at least one ring element.
  • the through openings formed by the ring elements allow the installation of a spark plug or an injection device.
  • double ignition can be implemented, in which case two valves are then preferably arranged per cylinder.
  • the contour of the upper part of the carrier is adapted to that of the lower part of the carrier, ie it carries a corresponding number of ring elements in the central web and the upper parts of the bearings for the bearings of the camshafts are each arranged over the bridges of the lower part of the carrier which are designed as lower parts of the bearing.
  • stiffening ribs can be arranged in the upper girder part between the transverse webs. It can thus be used advantageously in both internal and externally ignited internal combustion engines with two or more valves per cylinder and single or double spark plug arrangement.
  • the invention provides great freedom in the valve position with respect to the combustion chamber and in the arrangement of the cylinder head screws.
  • an internal combustion engine with e.g. Four valves per cylinder, which are arranged spherically to the combustion chamber, do not meet the requirements and easy-to-access arrangement of the cylinder head screws with bucket tappet guides arranged in the cylinder head housing and, at the same time, demand for the smallest overall length of the internal combustion engine.
  • Cylinder head assembly first requires inserting the valves into the cylinder head housing and attaching the cylinder head bolts. Then the valve springs and the valve plates are attached. Following this, either the completely pre-assembled carrier can be screwed onto the cylinder head housing as a complete unit, or its individual parts can be assembled one after the other. In the latter case, the first will be Lower part of the carrier inserted and the tappets inserted into the receptacles. The camshafts are then inserted and the upper part of the beam is screwed onto the lower part of the beam, as is the entire beam on the cylinder head housing.
  • the carrier can be completely pre-assembled by machine and then mechanically attached to the cylinder head housing.
  • the cylinder head 1 of a multi-cylinder internal combustion engine has a cylinder head housing 3 arranged on a cylinder block 2 and a carrier 4 mounted thereon, in which camshafts 5 are arranged in bearings 6.
  • the cylinder head 1 has four spherically arranged valves 7 with springs 8 and spring plates 9 assigned to them.
  • the valves 7 are actuated by conical cams 10 directly via tappets 11.
  • the carrier 4 consists of a carrier upper part 12 and a carrier lower part 13.
  • the carrier 4 has a central web 15 running as a longitudinal web 14, which runs parallel to the crankshaft of the internal combustion engine and is formed in the carrier upper part 12 and in the carrier lower part 13.
  • the receptacles 17 are arranged coaxially with the central longitudinal axes V of the valves 7.
  • the central longitudinal axes N of the camshaft 5 run in the plane parting plane 20 running between the upper part 12 and the lower part 13.
  • the bearings 6 are each formed from the upper part 21 in the upper part 12 and the lower part 22 in the lower part 13.
  • Each receptacle 17 is connected to the lower support part 13 via at least one support 23.
  • the struts 16 run with the supports 23 below the parting plane 20.
  • the central web 15 widens in a ring shape to form a ring element 24, which in this case encloses a through opening 25 and is arranged concentrically to the cylinder longitudinal axis Z. It enables the insertion of a tube 26, which enables access to a spark plug 27.
  • a lubricant channel system is arranged in the carrier 4 and is connected to the lubricating oil circuit of the internal combustion engine.
  • This system comprises channels 28, 29, 30, the channels 28, 29 running within the upper carrier part 12 in the central web 15 and in the transverse webs 19 and the channels 30 being arranged in the supports 23.
  • the channel 28 is connected at an arbitrary point, not shown, to the lubricating oil circuit of the internal combustion engine and serves as a distributor for the lubricating oil into the channels 29, 30.
  • the passage openings 25 are evenly flowed around by the channel 28, so that in the area of the ring elements 24 the carrier lower part 13 connected channels 3O supply the receptacles 17 with lubricating oil for guiding the tappets.
  • channels 30 branch off from channel 28 and lead lubricating oil to the bearings 6 of the camshafts 5.
  • the bridges 18 are designed as ribs 31 between the receptacles 17 belonging to a cylinder. These ribs 31 can be omitted if the associated receptacles 17 are cast together directly at a small distance. Between two adjacent receptacles 17 belonging to adjacent cylinders, the bridges 18 are designed as the lower bearing parts 22. In the area of these lower bearing parts 22, the transverse webs 19 are arranged between the struts 16 and are made in one piece with the lower bearing parts 22.
  • the transverse webs 19 have projections 22 which ensure that the receptacles 17 lying adjacent to a transverse web 19 are rigidly connected to one another over their entire height.
  • the upper bearing parts 21 are formed in the part of the transverse webs 19 running in the upper part 12 of the support.
  • bores 33 are arranged in the upper carrier part 12, which together with further bores 33 in the lower carrier part 13 and in the cylinder head housing 3 enable screw connections 34, 35.
  • the cylinder head housing 3 When assembling the part described above, the cylinder head housing 3 is first fastened to the cylinder block 2 with cylinder head screws 36 after the valves 7 have been pushed into corresponding guides. Bores 37 are provided in the cylinder head housing for receiving the cylinder head screws 36. Then the springs 8 and the spring plate 9 are attached to the valves 7. At this time, the image shown in FIG. 1 in the section labeled A results for the entire cylinder head. Subsequently, as already mentioned in the introduction to the description, the carrier 4 fully equipped with the camshafts 5 and the tappets 11 can be assembled as a whole or in individual parts in succession. The latter option is described in more detail below.
  • the carrier lower part 13 is first placed on the cylinder head housing 3 at three contact surfaces 38, then the tappets 11 are pushed into the receptacles 17.
  • the result shown in the section labeled B in FIG. 1 results for the entire cylinder head.
  • the upper carrier part 12 is fixed to the lower carrier part 13 with the screw connections 34.
  • the screw connections 35 penetrate the contact surfaces 38 and clamp the carrier lower part 13 between the cylinder head housing 3 and the upper carrier part 12 and fasten the carrier 4 in the cylinder head 1 (section D in FIG. 1).
  • a hood 39 is placed on the cylinder head 1.
  • This hood 39 surrounds the carrier 4 in a U-shape and lies on a flange 40 which can be machined together with the contact surfaces 38.
  • the surface between the hood 39 and the flange 40 is completely flat and has no bores, so that a simple seal is possible.
  • the tube 26 is inserted into the passage opening 25 and seals the spark plug area by means of two seals 41 in an opening 42 of the hood 39 and in a holder 43 in the cylinder head housing 3.
  • the arrangement of the screw connections 34, 35 in the plane in which the cylinder head screws are arranged enables an optimal, load-appropriate application of force from the carrier 4 to the cylinder block 2.
  • the invention can also be advantageous in internal combustion engines with e.g. two or three valves per cylinder can be used.
  • the corresponding receptacles 17 lie opposite one another in a plane which is parallel to and in the middle of two transverse webs 19.
  • two receptacles 17 advantageously lie diagonally opposite one another between two transverse webs 19.
  • the central web 15 then has two ring elements 24 for each cylinder, which can also lie diagonally opposite one another.
  • the transverse webs 19 are arranged above each cylinder of the internal combustion engine and each take on an annular element 24.
  • two receptacles 17 assigned to a cylinder are cast together below a lower bearing part 22 which acts as a bridge 18.
  • Two adjacent receptacles 17 belonging to adjacent cylinders are connected by a rib 31.

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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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Der Zylinderkopf (1) einer Brennkraftmaschine umfaßt einen horizontal geteilten (4) Träger, in dem Nockenwellenlager (6) sowie Aufnahmen (7) für Tassenstößel angeordnet sind. Die Anordnung ist durch Längs- (14) und Querstege (19) steif ausgeführt und ermöglicht durch das Herauslösen der Aufnahmen aus dem Zylindergehäuse ein einfaches Gußverfahren für das Zylinderkopfgehäuse. <IMAGE>The cylinder head (1) of an internal combustion engine comprises a horizontally divided (4) support in which camshaft bearings (6) and receptacles (7) for cup tappets are arranged. The arrangement is stiff with longitudinal (14) and transverse webs (19) and enables a simple casting process for the cylinder head housing by removing the receptacles from the cylinder housing. <IMAGE>

Description

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

Aus der DE- 36 41 129 C1 ist ein Nockenwellen- Lagerrahmen für eine Reihenbrennkraftmaschine mit vier Ventilen pro Zylinder bekannt, welcher als separates Teil auf das Zylinderkopfgrundgehäuse aufgeschraubt wird. Dieser Lagerrahmen besteht aus einem Gußteil mit zwischen den Zylindern und an den beiden Enden des Zylinderkopfes quer zur Längsrichtung verlaufenden Stegen sowie mit zwei in Längsrichtung parallel verlaufenden Stegen, die auf den seitlichen Gehäusewänden des Zylinderkopfes aufliegen. In den quer verlaufenden Stegen sind untere Lagerhalbschalen für die Lager von Nockenwellen ausgebildet, deren obere Hälften durch voneinander getrennte, auf den Nockenwellen-Lagerrahmen aufschraubbare Lagerdeckel gebildet werden. Dieser Lagerrahmen ermöglicht eine separate Vormontage der Nockenwellen mit ihren Lagern. Nachteilig bei dieser Ausführung ist, daß trotz der separaten Nockenwellenlagerung ein aufwendig gestaltetes Zylinderkopfgehäuse verbleibt, das z.B. aufgrund der darin angeordneten Aufnahmen für die Tassenstößel Hinterschneidungen aufweist und somit nur mit verlorenem Kern gegossen werden kann. Das dabei entstehende Gefüge und die Oberfläche sind bezüglich der Festigkeit nicht optimal.
In der DE 38 19 655 ist ein Vierventil-Zylinderkopf für eine Brennkraftmaschine offenbart, in der die Aufnahmen für die Tassenstößel paarweise brillenartig zusammengefaßt sind. Dieser Zylinderkopf weist eine komplizierte Formgebung auf, die aufgrund der vielen Hinterschneidungen auf der der Brennraumseite gegenüberliegenden Deckseite ein Sandgußverfahren erforderlich macht. Dieses Verfahren benötigt eine gründliche und zeitaufwendige Reinigung der Deckseite nach dem Gießen.From DE-36 41 129 C1 a camshaft bearing frame for an internal combustion engine with four valves per cylinder is known, which is screwed onto the cylinder head base housing as a separate part. This bearing frame consists of a cast part with webs running transversely to the longitudinal direction between the cylinders and at the two ends of the cylinder head, and with two webs running parallel in the longitudinal direction, which rest on the lateral housing walls of the cylinder head. Lower half-shells for the bearings of camshafts are formed in the transverse webs, the upper halves of which are formed by separate bearing covers which can be screwed onto the camshaft bearing frame. This bearing frame enables the camshafts and their bearings to be pre-assembled separately. A disadvantage of this design is that, despite the separate camshaft bearing, an elaborately designed cylinder head housing remains which, for example, has undercuts due to the receptacles arranged therein for the tappets and can therefore only be cast with a lost core. The resulting structure and the surface are not optimal in terms of strength.
DE 38 19 655 discloses a four-valve cylinder head for an internal combustion engine, in which the receptacles for the tappets are combined in pairs in the form of glasses. This cylinder head has a complicated shape, which requires a sand casting process due to the many undercuts on the top side opposite the combustion chamber side. This process requires thorough and time-consuming cleaning of the top side after casting.

Es ist die Aufgabe der Erfindung, einen Zylinderkopf hoher Steifigkeit für eine Brennkraftmaschine zu schaffen, der die vorgenannten Nachteile vermeidet und es somit ermöglicht, diesen Zylinderkopf in einem einfachen Gußverfahren herzustellen. Weiterhin soll dieser Zylinderkopf maschinell montierbar sein. Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst. Weitere, die Erfindung vorteilhaft ausgestaltende Merkmale enthalten die Unteransprüche. Von besonderem Vorteil bei dieser Erfindung ist es, daß sowohl die Nockenwellenlagerung als auch die der Führung der Tassenstößel dienenden Aufnahmen aus dem Zylinderkopfgehäuse herausgelöst sind. Dadurch ist die dem Brennraum zugewandte Unterseite und die dieser Unterseite gegenüberliegende Zylinderkopfdeckseite aufgrund der einfachen Formgebung in einem gemeinsamen Gußverfahren, z.B. Kokillenguß herstellbar. Das dabei entstehende Gußgefüge weist eine große Homogenität und gegenüber den bekannten Lösungen verbesserte Werkstoffkennwerte auf. Das Risiko von Rißbildungen im Zylinderkopfgehäuse ist dadurch deutlich verringert.
Der Träger ist unabhängig vom Zylinderkopfgehäuse im Druckgußverfahren herstellbar und anschließend kostengünstig zu bearbeiten. Trägerober- und -unterteil umfassen jeweils Teile eines Mittelsteges sowie Teile von mehreren Querstegen. Zur Aussteifung der Querstege sind keine gesonderten, gewichtserhöhenden Längsstege im Träger angeordnet, vielmehr wird diese Funktion von beiderseits des Mittelsteges im Trägerunterteil verlaufenden Streben übernommen, die Tassenstößel führende Aufnahmen umfassen, welche untereinander über Brücken verbunden sind. Jede Aufnahme ist wiederum über mindestens eine Stütze an dem im Trägerunterteil verlaufenden Teil des Mittelsteges abgestützt. Bei einer bevorzugten Anwendung gemäß Anspruch 9 in einer Brennkraftmaschine mit jeweils zwei Einlaß- und zwei Auslaßventilen pro Zylinder sind die der Tassenstößellagerung dienenden, paarweise zusammenwirkenden Aufnahmen eines Zylinders über eine als Rippe ausgebildete Brücke miteinander verbunden, während die Brücke zwischen zu benachbarten Zylindern gehörende Aufnahmen als Lagerunterteile von Lagern für zwei Nockenwellen ausgebildet ist. Somit entsteht ein leichtgewichtiger, steifer Träger, dessen Streben durch ihre Gestaltung zur Aussteifung des Trägers beitragen und als Lagerung für Tassenstößel wirken.
In einer anderen Ausführung der Erfindung gemäß Anspruch 10 sind die paarweise zusammenwirkenden Aufnahmen eines Zylinders über eine als Lagerunterteil eines Lagers einer Nockenwelle ausgebildete Brücke verbunden, wobei die Brücke zwischen zu benachbarten Zylindern gehörende Aufnahmen über eine als Rippe ausgebildete Brücke verbunden sind.
In beiden Ausführungen der Erfindung erweitert sich der Mittelsteg oberhalb jedes Zylinders kreisringförmig zu mindestens einem Ringelement. Die von den Ringelementen gebildeten Durchgangsöffnungen gestatten das Montieren einer Zündkerze oder einer Einspritzvorrichtung. Bei einer weiteren Ausführung mit zwei Ringelementen oberhalb jedes Zylinders läßt sich beispielsweise eine Doppelzündung realisieren, wobei dann bevorzugt zwei Ventile pro Zylinder angeordnet sind.
Bei allen Ausführungen der Erfindung ist die Kontur des Trägeroberteils der des Trägerunterteils angepaßt, d.h., es trägt eine dementsprechende Anzahl von Ringelementen im Mittelsteg und die Lageroberteile für die Lager der Nockenwellen sind jeweils über den als Lagerunterteil ausgebildeten Brücken des Trägerunterteils angeordnet. Zur weiteren Aussteifung des Trägers können im Trägeroberteil zwischen den Querstegen Versteifungsrippen angeordnet sein. Er ist somit vorteilhaft bei selbst- wie auch bei fremdgezündeten Brennkraftmaschinen mit zwei oder mehr Ventilen pro Zylinder sowie einfacher oder doppelter Zündkerzenanordnung verwendbar.It is the object of the invention to provide a cylinder head of high rigidity for an internal combustion engine which avoids the aforementioned disadvantages and thus makes it possible to produce this cylinder head in a simple casting process. Furthermore, this cylinder head should be mechanically mountable. This object is solved by the features of claim 1. Further features advantageously configuring the invention are contained in the subclaims. It is particularly advantageous with this invention that both the camshaft bearing and the receptacles used to guide the tappets are detached from the cylinder head housing. As a result, the underside facing the combustion chamber and the cylinder head cover side opposite this underside can be produced in a common casting process, for example permanent mold casting, due to the simple shape. The resulting cast structure has a high degree of homogeneity and improved material properties compared to the known solutions. This significantly reduces the risk of cracks in the cylinder head housing.
The carrier can be produced independently of the cylinder head housing using the die casting process and can then be machined inexpensively. Upper and lower girder sections each include parts of a central web and parts of several cross webs. To stiffen the crossbars, no separate, weight-increasing longitudinal webs are arranged in the carrier, rather this function is performed by struts running on both sides of the central web in the lower part of the carrier, which include tappet-guiding receptacles which are connected to one another by bridges. Each receptacle is in turn supported by at least one support on the part of the central web running in the lower part of the carrier. In a preferred application according to claim 9 in an internal combustion engine, each with two intake and two exhaust valves per cylinder, the tappet bearing, pair-cooperating receptacles of a cylinder are connected to one another via a bridge designed as a rib, while the bridge between receptacles belonging to adjacent cylinders as Bearing lower parts of bearings for two camshafts is formed. This creates a lightweight, stiff carrier, the struts of which contribute to stiffening the carrier and act as a bearing for cup tappets.
In another embodiment of the invention according to claim 10, the pairs of cooperating receptacles of a cylinder are connected via a bridge designed as a bearing lower part of a bearing of a camshaft, the bridge between receptacles belonging to adjacent cylinders being connected via a bridge designed as a rib.
In both embodiments of the invention, the central web extends in a ring shape above each cylinder to form at least one ring element. The through openings formed by the ring elements allow the installation of a spark plug or an injection device. In a further embodiment with two ring elements above each cylinder, for example, double ignition can be implemented, in which case two valves are then preferably arranged per cylinder.
In all embodiments of the invention, the contour of the upper part of the carrier is adapted to that of the lower part of the carrier, ie it carries a corresponding number of ring elements in the central web and the upper parts of the bearings for the bearings of the camshafts are each arranged over the bridges of the lower part of the carrier which are designed as lower parts of the bearing. To further stiffen the girder, stiffening ribs can be arranged in the upper girder part between the transverse webs. It can thus be used advantageously in both internal and externally ignited internal combustion engines with two or more valves per cylinder and single or double spark plug arrangement.

Ein weiterer, wichtiger Vorteil ist darin zu sehen, daß durch die Erfindung große Freiheiten bei der Ventillage bezüglich des Brennraumes sowie bei der Anordnung der Zylinderkopfschrauben gegeben sind. Bei einer Brennkraftmaschine mit z.B. vier Ventilen pro Zylinder, die sphärisch zum Brennraum angeordnet sind, ist eine beanspruchungsgerechte und leicht zugängliche Anordnung der Zylinderkopfschrauben bei im Zylinderkopfgehäuse angeordneten Tassenstößelführungen und gleichzeitiger Forderung nach geringster Baulänge der Brennkraftmaschine nicht zu erfüllen. Erst das erfindungsgemäße Herauslösen der Nockenwellenlagerung und der Tassenstößel ermöglicht freie Zugänglichkeit zu den Bohrungen im Zylinderkopfgehäuse, die der Durchgangsöffnung der Zylinderkopfschrauben dienen und ermöglicht eine belastungsgerechte Anordnung dieser Bohrungen in Bereichen maximaler Festigkeit des darunterliegenden Zylinderblockes.Another important advantage can be seen in the fact that the invention provides great freedom in the valve position with respect to the combustion chamber and in the arrangement of the cylinder head screws. In an internal combustion engine with e.g. Four valves per cylinder, which are arranged spherically to the combustion chamber, do not meet the requirements and easy-to-access arrangement of the cylinder head screws with bucket tappet guides arranged in the cylinder head housing and, at the same time, demand for the smallest overall length of the internal combustion engine. It is only when the camshaft bearing and the tappets are removed that the holes in the cylinder head housing, which are used for the through-opening of the cylinder head bolts, are freely accessible, and these holes can be arranged in a manner appropriate to the load in areas of maximum strength of the cylinder block underneath.

Die Zylinderkopfmontage erfordert zunächst das Einführen der Ventile in das Zylinderkopfgehäuse und das Anbringen der Zylinderkopfschrauben. Anschließend werden die Ventilfedern sowie die Ventilteller angebracht. Im Anschluß daran kann entweder der komplett vormontierte Träger als gesamte Einheit auf das Zylinderkopfgehäuse geschraubt werden oder aber dessen Einzelteile aufeinanderfolgend montiert werden. Im letzteren Fall werden zunächst das Trägerunterteil eingelegt und die Tassenstößel in die Aufnahmen geführt. Anschließend werden die Nockenwellen eingelegt und das Trägeroberteil auf das Trägerunterteil geschraubt, ebenso wie der gesamte Träger auf das Zylinderkopfgehäuse.Cylinder head assembly first requires inserting the valves into the cylinder head housing and attaching the cylinder head bolts. Then the valve springs and the valve plates are attached. Following this, either the completely pre-assembled carrier can be screwed onto the cylinder head housing as a complete unit, or its individual parts can be assembled one after the other. In the latter case, the first will be Lower part of the carrier inserted and the tappets inserted into the receptacles. The camshafts are then inserted and the upper part of the beam is screwed onto the lower part of the beam, as is the entire beam on the cylinder head housing.

Der Träger kann komplett maschinell vormontiert werden und anschließend maschinell am Zylinderkopfgehäuse angebracht werden.The carrier can be completely pre-assembled by machine and then mechanically attached to the cylinder head housing.

Ein bevorzugtes Ausführungsbeispiel der Erfindung wird anhand der nachfolgend aufgeführten Figuren erläutert.A preferred embodiment of the invention is explained with reference to the figures listed below.

Es zeigt

Fig. 1
eine Draufsicht eines Zylinderkopfes, unterteilt in aufeinander folgende Abschnitte der Montage,
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
Fig. 5
eine weitere Ausführung der Erfindung.
It shows
Fig. 1
a plan view of a cylinder head, divided into successive sections of the assembly,
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 FIG. 1st
Fig. 5
a further embodiment of the invention.

Der Zylinderkopf 1 einer mehrzylindrigen Brennkraftmaschine weist ein auf einem Zylinderblock 2 angeordnetes Zylinderkopfgehäuse 3 und einen darauf montieren Träger 4 auf, in dem Nockenwellen 5 in Lagern 6 angeordnet sind. Der Zylinderkopf 1 weist pro Zylinder vier sphärisch angeordnete Ventile 7 mit ihnen zugeordneten Federn 8 und Federtellern 9 auf. Die Ventile 7 werden von konischen Nocken 10 unmittelbar über Tassenstößel 11 betätigt. Die Mittellängsachsen V der Ventile 7, entlang derer die Ventile 7 bewegt werden, schneiden die Mittellängsachsen N der jeweiligen Nockenwelle 5.
Der Träger 4 besteht aus einem Trägeroberteil 12 und einem Trägerunterteil 13. Ferner weist der Träger 4 einen als Längssteg 14 verlaufenden Mittelsteg 15 auf, der parallel zur Kurbelwelle der Brennkraftmaschine verläuft und im Trägeroberteil 12 sowie im Trägerunterteil 13 ausgebildet ist. Beiderseits des Mittelsteges 15 und parallel dazu beabstandet verlaufen im Trägerunterteil 13 Streben 16, die aus Aufnahmen 17 für die Tassenstößel 11 und diese Aufnahmen 17 verbindende Brücken 18 gebildet sind. Die Aufnahmen 17 sind koaxial zu den Mittellängsachsen V der Ventile 7 angeordnet.
Quer zu dem Mittelsteg 15 und den Streben 16 verlaufen Querstege 19, die im Trägeroberteil 12 und im Trägerunterteil 13 ausgebildet sind. In der zwischen Trägeroberteil 12 und Trägerunterteil 13 verlaufenden, planen Trennebene 20 verlaufen die Mittellängsachsen N der Nockenwelle 5. Die Lager 6 sind jeweils aus Lageroberteil 21 im Trägeroberteil 12 und als Lagerunterteil 22 im Trägerunterteil 13 gebildet.
Jede Aufnahme 17 ist über mindestens eine Stütze 23 am Trägerunterteil 13 angebunden. Die Streben 16 verlaufen mit den Stützen 23 unterhalb der Trennebene 20.
Oberhalb jedes Zylinders der Brennkraftmaschine erweitet sich der Mittelsteg 15 kreisringförmig zu einem Ringelement 24, welches dabei eine Durchgangsöffnung 25 umschließt und konzentrisch zur Zylinderlängsachse Z angeordnet ist. Sie ermöglicht das Einschieben eines Tubus 26, der den Zugang zu einer Zündkerze 27 ermöglicht.
Im Träger 4 ist ein Schmiermittelkanalsystem angeordnet, welches an den Schmierölkreislauf der Brennkraftmaschine angeschlossen ist. Dieses System umfaßt Kanäle 28, 29, 30, wobei die Kanäle 28, 29 innerhalb des Trägeroberteiles 12 im Mittelsteg 15 und in den Querstegen 19 verlaufen und die Kanäle 30 in den Stützen 23 angeordnet sind. Der Kanal 28 ist an einer nicht gezeigten, beliebigen Stelle an den Schmierölkreislauf der Brennkraftmaschine angeschlossen und dient als Verteiler für das Schmieröl in die Kanäle 29, 30. Die Durchgangsöffnungen 25 werden vom Kanal 28 gleichmäßig umströmt, so daß die im Bereich der Ringelemente 24 an das Trägerunterteil 13 angeschlossene Kanäle 3O die Aufnahmen 17 mit Schmieröl zur Führung der Tassenstößel versorgen. Im Bereich der Querstege 19 zweigen Kanäle 30 vom Kanal 28 ab und führen Schmieröl zu den Lagern 6 der Nockenwellen 5.
Die Brücken 18 sind zwischen den zu einem Zylinder gehörenden Aufnahmen 17 als Rippen 31 ausgeführt. Diese Rippen 31 können entfallen, wenn bei einem geringen Abstand der zugehörigen Aufnahmen 17 diese direkt zusammengegossen werden.
Zwischen zwei nebeneinanderliegenden, zu benachbarten Zylindern gehörenden Aufnahmen 17 sind die Brücken 18 als die Lagerunterteile 22 ausgeführt. Im Bereich dieser Lagerunterteile 22 sind zwischen den Streben 16 verlaufend die Querstege 19 angeordnet und einteilig mit den Lagerunterteilen 22 ausgeführt. Unterhalb der Lagerunterteile 22 weisen die Querstege 19 Vorsprünge 22 auf, die dafür sorgen, daß die benachbart eines Quersteges 19 liegenden Aufnahmen 17 über ihre gesamte Bauhöhe steif miteinander verbunden sind.
In dem im Trägeroberteil 12 verlaufenden Teil der Querstege 19 sind die Lageroberteile 21 ausgebildet. Beiderseits der Lageroberteile 21 und im Bereich des Mittelsteges 15 sind im Trägeroberteil 12 Bohrungen 33 angeordnet, die gemeinsam mit weiteren Bohrungen 33 im Trägerunterteil 13 und im Zylinderkopfgehäuse 3 Schraubverbindungen 34, 35 ermöglichen.The cylinder head 1 of a multi-cylinder internal combustion engine has a cylinder head housing 3 arranged on a cylinder block 2 and a carrier 4 mounted thereon, in which camshafts 5 are arranged in bearings 6. The cylinder head 1 has four spherically arranged valves 7 with springs 8 and spring plates 9 assigned to them. The valves 7 are actuated by conical cams 10 directly via tappets 11. The central longitudinal axes V of the valves 7, along which the valves 7 are moved, intersect the central longitudinal axes N of the respective camshaft 5.
The carrier 4 consists of a carrier upper part 12 and a carrier lower part 13. Furthermore, the carrier 4 has a central web 15 running as a longitudinal web 14, which runs parallel to the crankshaft of the internal combustion engine and is formed in the carrier upper part 12 and in the carrier lower part 13. Struts 16, which are formed from receptacles 17 for the cup tappets 11 and bridges 18 connecting these receptacles 17, run in the lower carrier part 13 on both sides of the central web 15 and spaced parallel to them. The receptacles 17 are arranged coaxially with the central longitudinal axes V of the valves 7.
Cross webs 19, which are formed in the upper carrier part 12 and in the lower carrier part 13, run transversely to the central web 15 and the struts 16. The central longitudinal axes N of the camshaft 5 run in the plane parting plane 20 running between the upper part 12 and the lower part 13. The bearings 6 are each formed from the upper part 21 in the upper part 12 and the lower part 22 in the lower part 13.
Each receptacle 17 is connected to the lower support part 13 via at least one support 23. The struts 16 run with the supports 23 below the parting plane 20.
Above each cylinder of the internal combustion engine, the central web 15 widens in a ring shape to form a ring element 24, which in this case encloses a through opening 25 and is arranged concentrically to the cylinder longitudinal axis Z. It enables the insertion of a tube 26, which enables access to a spark plug 27.
A lubricant channel system is arranged in the carrier 4 and is connected to the lubricating oil circuit of the internal combustion engine. This system comprises channels 28, 29, 30, the channels 28, 29 running within the upper carrier part 12 in the central web 15 and in the transverse webs 19 and the channels 30 being arranged in the supports 23. The channel 28 is connected at an arbitrary point, not shown, to the lubricating oil circuit of the internal combustion engine and serves as a distributor for the lubricating oil into the channels 29, 30. The passage openings 25 are evenly flowed around by the channel 28, so that in the area of the ring elements 24 the carrier lower part 13 connected channels 3O supply the receptacles 17 with lubricating oil for guiding the tappets. In the area of the transverse webs 19, channels 30 branch off from channel 28 and lead lubricating oil to the bearings 6 of the camshafts 5.
The bridges 18 are designed as ribs 31 between the receptacles 17 belonging to a cylinder. These ribs 31 can be omitted if the associated receptacles 17 are cast together directly at a small distance.
Between two adjacent receptacles 17 belonging to adjacent cylinders, the bridges 18 are designed as the lower bearing parts 22. In the area of these lower bearing parts 22, the transverse webs 19 are arranged between the struts 16 and are made in one piece with the lower bearing parts 22. Below the lower bearing parts 22, the transverse webs 19 have projections 22 which ensure that the receptacles 17 lying adjacent to a transverse web 19 are rigidly connected to one another over their entire height.
The upper bearing parts 21 are formed in the part of the transverse webs 19 running in the upper part 12 of the support. On both sides of the upper bearing parts 21 and in the region of the central web 15, bores 33 are arranged in the upper carrier part 12, which together with further bores 33 in the lower carrier part 13 and in the cylinder head housing 3 enable screw connections 34, 35.

Beim Zusammenbau des zuvor beschriebenen Teiles wird zunächst das Zylinderkopfgehäuse 3 mit Zylinderkopfschrauben 36 am Zylinderblock 2 befestigt, nachdem die Ventile 7 in entsprechende Führungen geschoben wurden. Zur Aufnahme der Zylinderkopfschrauben 36 sind im Zylinderkopfgehäuse Bohrungen 37 vorgesehen. Anschließend werden die Federn 8 und die Federteller 9 an den Ventilen 7 angebracht. Zu diesem Zeitpunkt ergibt sich das in Fig. 1 in dem mit A bezeichneten Abschnitt dargestellte Bild für den gesamten Zylinderkopf. Im Anschluß daran kann, wie bereits in der Beschreibungseinleitung erwähnt, der komplett mit den Nockenwellen 5 und den Tassenstößeln 11 bestückte Träger 4 als gesamte Einheit oder aber in Einzelteilen aufeinanderfolgend montiert werden. Letzere Möglichkeit wird im folgenden näher beschrieben.When assembling the part described above, the cylinder head housing 3 is first fastened to the cylinder block 2 with cylinder head screws 36 after the valves 7 have been pushed into corresponding guides. Bores 37 are provided in the cylinder head housing for receiving the cylinder head screws 36. Then the springs 8 and the spring plate 9 are attached to the valves 7. At this time, the image shown in FIG. 1 in the section labeled A results for the entire cylinder head. Subsequently, as already mentioned in the introduction to the description, the carrier 4 fully equipped with the camshafts 5 and the tappets 11 can be assembled as a whole or in individual parts in succession. The latter option is described in more detail below.

Das Trägerunterteil 13 wird zunächst an drei Berührungsflächen 38 auf das Zylinderkopfgehäuse 3 gelegt, anschließend werden die Tassenstößel 11 in die Aufnahmen 17 geschoben. Es ergibt sich das in dem mit B bezeichneten Abschnitt in Fig. 1 dargestellte Bild für den gesamten Zylinderkopf.The carrier lower part 13 is first placed on the cylinder head housing 3 at three contact surfaces 38, then the tappets 11 are pushed into the receptacles 17. The result shown in the section labeled B in FIG. 1 results for the entire cylinder head.

Nach dem einlegen der Nockenwellen 5 in die Lagerunterteile 22 (Abschnitt C in Fig. 1) wird das Trägeroberteil 12 mit den Schraubverbindungen 34 am Trägerunterteil 13 fixiert. Die Schraubverbindungen 35 durchdringen die Berührungsflächen 38 und verspannen das Trägerunterteil 13 zwischen Zylinderkopfgehäuse 3 und Trägeroberteil 12 und befestigen den Träger 4 im Zylinderkopf 1 (Abschnitt D in Fig. 1). Abschließend wird eine Haube 39 auf den Zylinderkopf 1 aufgesetzt. Diese Haube 39 umschließt den Träger 4 U-förmig und liegt auf einem Flansch 40 auf, der gemeinsam mit den Berührungsflächen 38 bearbeitet werden kann. Vorteilhafterweise ist die zwischen Haube 39 und Flansch 40 liegende Fläche völlig plan und weist keinerlei Bohrungen auf, so daß eine einfach Abdichtung möglich ist.After inserting the camshafts 5 into the lower bearing parts 22 (section C in FIG. 1), the upper carrier part 12 is fixed to the lower carrier part 13 with the screw connections 34. The screw connections 35 penetrate the contact surfaces 38 and clamp the carrier lower part 13 between the cylinder head housing 3 and the upper carrier part 12 and fasten the carrier 4 in the cylinder head 1 (section D in FIG. 1). Finally, a hood 39 is placed on the cylinder head 1. This hood 39 surrounds the carrier 4 in a U-shape and lies on a flange 40 which can be machined together with the contact surfaces 38. Advantageously, the surface between the hood 39 and the flange 40 is completely flat and has no bores, so that a simple seal is possible.

In die Durchgangsöffnung 25 wird der Tubus 26 gesteckt, der den Zündkerzenbereich mittels zweier Dichtungen 41 in einer Öffnung 42 der Haube 39 und in einer Haltung 43 im Zylinderkopfgehäuse 3 abdichtet. Die Anordnung der Schraubverbindungen 34, 35 in der Ebene, in der die Zylinderkopfschrauben angeordnet sind, ermöglicht eine optimale, belastungsgerechte Krafteinleitung vom Träger 4 bis in den Zylinderblock 2.The tube 26 is inserted into the passage opening 25 and seals the spark plug area by means of two seals 41 in an opening 42 of the hood 39 and in a holder 43 in the cylinder head housing 3. The arrangement of the screw connections 34, 35 in the plane in which the cylinder head screws are arranged enables an optimal, load-appropriate application of force from the carrier 4 to the cylinder block 2.

Wie in der Beschreibungseinleitung erwähnt, kann die Erfindung auch vorteilhaft bei Brennkraftmaschinen mit z.B. zwei oder drei Ventilen pro Zylinder angewendet werden. Bei zwei Ventilen 7 liegen sich die entsprechenden Aufnahmen 17 in einer Ebene gegenüber, die parallel zu und in der Mitte von zwei Querstegen 19 liegt. In einer Ausführung mit Doppelzündung und zwei Ventilen, liegen sich vorteilhafterweise zwei Aufnahmen 17 zwischen zwei Querstegen 19 diagonal gegenüber. Der Mittelsteg 15 weist dann für jeden Zylinder zwei Ringelemente 24 auf, welche sich ebenfalls diagonal gegenüberliegen können.As mentioned in the introduction to the description, the invention can also be advantageous in internal combustion engines with e.g. two or three valves per cylinder can be used. In the case of two valves 7, the corresponding receptacles 17 lie opposite one another in a plane which is parallel to and in the middle of two transverse webs 19. In an embodiment with double ignition and two valves, two receptacles 17 advantageously lie diagonally opposite one another between two transverse webs 19. The central web 15 then has two ring elements 24 for each cylinder, which can also lie diagonally opposite one another.

Gemäß Fig. 5 sind bei einer weiteren Ausführung der Erfindung die Querstege 19 oberhalb jedes Zylinders der Brennkraftmaschine angeordnet und nehmen dabei jeweils ein Ringelement 24 auf. Jeweils zwei einem Zylinder zugeordnete Aufnahmen 17 sind unterhalb eines als Brücke 18 wirkenden Lagerunterteiles 22 zusammengegossen. Zwei nebeneinanderliegende, zu benachbarten Zylindern gehörende Aufnahmen 17 sind durch eine Rippe 31 verbunden.5, in a further embodiment of the invention, the transverse webs 19 are arranged above each cylinder of the internal combustion engine and each take on an annular element 24. In each case two receptacles 17 assigned to a cylinder are cast together below a lower bearing part 22 which acts as a bridge 18. Two adjacent receptacles 17 belonging to adjacent cylinders are connected by a rib 31.

Claims (16)

Zylinderkopf einer mehrzylindrigen Brennkraftmaschine mit einem geteilten Träger zur Aufnahme von Nockenwellen, die über Tassenstößel auf Ventile wirken, wobei der Lager für die Nockenwellen aufweisende Träger vom Zylinderkopfgehäuse lösbar ausgebildet ist und in Richtung der Kurbelwelle parallel und beabstandet zueinander verlaufende Längsstege und rechtwinklig dazu verlaufende Querstege aufweist, dadurch gekennzeichnet, daß der Träger (4) als Längsstege (14) verlaufende Streben (16) aufweist, wobei die Streben (16) aus Aufnahmen (17) für die Tassenstößel (11) und diese Aufnahmen (17) verbindende Brücken (18) gebildet sind.Cylinder head of a multi-cylinder internal combustion engine with a divided carrier for receiving camshafts, which act on valves via bucket tappets, the bearing for the camshaft-bearing carrier being detachable from the cylinder head housing and having longitudinal webs running parallel and spaced apart from one another and having transverse webs running at right angles thereto characterized in that the carrier (4) has struts (16) running as longitudinal webs (14), the struts (16) consisting of receptacles (17) for the cup tappets (11) and bridges (18) connecting these receptacles (17) are formed. Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß die Aufnahmen (17) jeweils mittels zweier Brücken (18) in einer Strebe (16) gehalten sind, wobei die ersten Brücken (18) als Lagerunterteile (22) der Lager (20) für die Nockenwellen (5) und die zweiten Brücken (18) als Rippen (31) ausgebildet sind.Cylinder head according to claim 1, characterized in that the receptacles (17) are each held in a strut (16) by means of two bridges (18), the first bridges (18) as bearing lower parts (22) of the bearings (20) for the camshafts (5) and the second bridges (18) are designed as ribs (31). Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß in dem Träger (4) zwischen zwei Streben (16) ein als Längssteg (14) verlaufender Mittelsteg (15) angeordnet ist.Cylinder head according to claim 1, characterized in that a central web (15) extending as a longitudinal web (14) is arranged in the carrier (4) between two struts (16). Zylinderkopf nach Anspruch 3, dadurch gekennzeichnet, daß der Mittelsteg (15) und die Querstege (19) jeweils in einem den Träger (4) bildenden Trägeroberteil (12) und Trägerunterteil (13) ausgebildet sind.Cylinder head according to Claim 3, characterized in that the central web (15) and the cross webs (19) are each formed in a top part (12) and bottom part (13) forming the part (4). Zylinderkopf nach Anspruch 4, dadurch gekennzeichnet, daß die Streben (16) im Trägerunterteil (13) ausgebildet sind.Cylinder head according to claim 4, characterized in that the struts (16) are formed in the lower carrier part (13). Zylinderkopf nach Anspruch 3, dadurch gekennzeichnet, daß sich der Mittelsteg (15) oberhalb jedes Zylinders der Brennkraftmaschine kreisringförmig zu mindestens einem Ringelement (24) erweitert und dabei jeweils eine Durchgangsöffnung (25) umschließt.Cylinder head according to claim 3, characterized in that the central web (15) is above each cylinder of the internal combustion engine expanded in a ring shape to at least one ring element (24) and thereby encloses one through opening (25). Zylinderkopf nach Anspruch 4, dadurch gekennzeichnet, daß in den Querstegen (19) erste das Trägeroberteil (12) und das Trägerunterteil (13) miteinander verbindende Schraubverbindungen (34) und zweite, den Träger (4) am Zylinderkopfgehäuse (3) haltende Schraubverbindungen (35) angeordnet sind.Cylinder head according to claim 4, characterized in that in the transverse webs (19) first screw connections (34) connecting the upper support part (12) and the lower support part (13) and second screw connections (35) holding the support (4) on the cylinder head housing (3) ) are arranged. Zylinderkopf nach Anspruch 7, dadurch gekennzeichnet, daß die Aufnahmen (17) koaxial zu den Mittellängsachsen (V) der Ventile (7) angeordnet sind.Cylinder head according to claim 7, characterized in that the receptacles (17) are arranged coaxially to the central longitudinal axes (V) of the valves (7). Zylinderkopf nach Anspruch 2, dadurch gekennzeichnet, daß jeweils zwei benachbarte, über eine Rippe (31) verbundene Aufnahmen (17) oberhalb eines Zylinders der Brennkraftmaschine angeordnet sind (Fig. 1).Cylinder head according to claim 2, characterized in that two adjacent receptacles (17) connected via a rib (31) are arranged above a cylinder of the internal combustion engine (Fig. 1). Zylinderkopf nach Anspruch 2, dadurch gekennzeichnet, daß jeweils zwei benachbarte, über ein Lagerunterteil (22) verbundene Aufnahmen (17) oberhalb eines Zylinders der Brennkraftmaschine angeordnet sind (Fig. 5).Cylinder head according to claim 2, characterized in that two adjacent receptacles (17) connected via a lower bearing part (22) are arranged above a cylinder of the internal combustion engine (Fig. 5). Zylinderkopf nach Anspruch 6 und 9, dadurch gekennzeichnet, daß die Querstege (19) zwischen benachbarten Ringelementen (24) verlaufen und daß die Querstege (19) Lagerunterteile (22) umfassen (Fig. 1).Cylinder head according to claims 6 and 9, characterized in that the crosspieces (19) run between adjacent ring elements (24) and that the crosspieces (19) comprise lower bearing parts (22) (Fig. 1). Zylinderkopf nach Anspruch 6 und 10, dadurch gekennzeichnet, daß oberhalb jedes Zylinders der Brennkraftmaschine ein Ringelement (24) koaxial zur Zylinderachse (Z) angeordnet ist und daß die Querstege (19) das Ringelement (24) umfassen.Cylinder head according to Claims 6 and 10, characterized in that a ring element (24) is arranged coaxially to the cylinder axis (Z) above each cylinder of the internal combustion engine, and in that the transverse webs (19) encompass the ring element (24). Zylinderkopf nach Anspruch 4, dadurch gekennzeichnet, daß jede Aufnahme (17) eine Stütze (23) aufweist, die aus einem Stück mit dem Trägerunterteil (13) gebildet und an den Mittelsteg (15) angebunden ist.Cylinder head according to Claim 4, characterized in that each receptacle (17) has a support (23) which is formed in one piece with the lower carrier part (13) and is connected to the central web (15). Zylinderkopf nach Anspruch 1, dadurch gekennzeichnet, daß in dem Träger (4) ein die Lager (20) und die Aufnahmen (17) versorgendes, Kanäle (28, 29, 30) umfassendes Schmiermittelkanalsystem angeordnet ist.Cylinder head according to Claim 1, characterized in that a lubricant channel system comprising channels (28, 29, 30) supplying the bearings (20) and the receptacles (17) is arranged in the carrier (4). Zylinderkopf nach Anspruch 4 und 15, dadurch gekennzeichnet, daß der Kanal (28) im Mittelsteg (15) oberhalb der zwischen Trägeroberteil (12) und Trägerunterteil (13) verlaufenden Ebene (20) angeordnet ist und daß die Kanäle (29) oberhalb dieser Ebene (20) in den Querstegen (19) von dem Kanal (28) abzweigend angeordnet sind.Cylinder head according to Claims 4 and 15, characterized in that the channel (28) in the central web (15) is arranged above the plane (20) running between the upper beam part (12) and the lower beam part (13) and that the channels (29) are above this plane (20) are arranged in the transverse webs (19) branching from the channel (28). Zylinderkopf nach Anspruch 14 und 16, dadurch gekennzeichnet, daß die Kanäle (30) mittig in den Stützen (23) verlaufend angeordnet sind und an den im Ringelement (24) verlaufenden Kanal (28) angeschlossen sind.Cylinder head according to Claims 14 and 16, characterized in that the channels (30) are arranged running centrally in the supports (23) and are connected to the channel (28) running in the ring element (24).
EP90116952A 1989-12-11 1990-09-04 Cylinder head for internal-combustion engine Expired - Lifetime EP0436779B1 (en)

Applications Claiming Priority (2)

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DE3940845 1989-12-11
DE3940845A DE3940845C1 (en) 1989-12-11 1989-12-11

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JP (1) JPH0491351A (en)
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Also Published As

Publication number Publication date
DE3943727A1 (en) 1994-02-10
US5080057A (en) 1992-01-14
DE59004034D1 (en) 1994-02-10
EP0436779B1 (en) 1993-12-29
DE3943729A1 (en) 1994-02-17
DE3943729C2 (en) 1995-07-13
ES2047785T3 (en) 1994-03-01
DE3943728C2 (en) 1995-07-13
DE3943728A1 (en) 1994-02-10
JPH0491351A (en) 1992-03-24
DE3943727C2 (en) 1995-07-13
DE3940845C1 (en) 1990-08-09

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