EP0356641A2 - Cooling system for the valve seats in the cylinder head of an internal-combustion engine - Google Patents

Cooling system for the valve seats in the cylinder head of an internal-combustion engine Download PDF

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Publication number
EP0356641A2
EP0356641A2 EP89111053A EP89111053A EP0356641A2 EP 0356641 A2 EP0356641 A2 EP 0356641A2 EP 89111053 A EP89111053 A EP 89111053A EP 89111053 A EP89111053 A EP 89111053A EP 0356641 A2 EP0356641 A2 EP 0356641A2
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EP
European Patent Office
Prior art keywords
ring
cooling
channel
camshaft
valve seat
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
EP89111053A
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German (de)
French (fr)
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EP0356641A3 (en
EP0356641B1 (en
Inventor
Michael Beer
Philipp Schimko
August Dipl.-Ing. Hofbauer
Matthias Dipl.-Ing. Kröner
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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Publication of EP0356641A3 publication Critical patent/EP0356641A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/12—Arrangements for cooling other engine or machine parts
    • F01P3/14—Arrangements for cooling other engine or machine parts for cooling intake or exhaust valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L3/22—Valve-seats not provided for in preceding subgroups of this group; Fixing of valve-seats
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P9/00—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00
    • 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
    • F01M9/101—Lubrication of valve gear or auxiliaries of cam surfaces
    • 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 
    • F02F1/24—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

Definitions

  • the invention relates to a valve seat ring cooling system according to the preamble of claim 1.
  • valve seats in particular the thermally highly loaded valve seat rings of exhaust valves of an internal combustion engine.
  • a valve seat ring cooling is known in which the cooling water used for cooling the internal combustion engine is used as the cooling medium.
  • the cooling water flows radially into the cooling channels of the valve seat rings and out through an opening opposite the inlet.
  • the drain openings open into a channel that leads directly into the suction side of the cooling water pump, which supplies the internal combustion engine with cooling water. This arrangement is not applicable when the internal combustion engine is air-cooled.
  • Cooling the valve seat rings of a liquid-cooled internal combustion engine independently of the main cooling circuit by another coolant, for example lubricating oil, in a separate cooling circuit is known from DE-05 15 76 727.
  • the coolant first flows to the outlet valve seat rings and from there to the seat rings Inlet valves. A uniform flow around the seat rings is not guaranteed due to the piping.
  • a separate coolant circuit with its own pump is required.
  • the object of the present invention is therefore to provide a cooling device for valve seat rings of an air-cooled internal combustion engine, which is connected to an existing lubricating oil circuit and through which an optimal and uniform cooling of all valve seat rings is achieved.
  • the feed and discharge lines can be easily produced as bores perpendicular to the separating surface between the cylinder head and the camshaft housing.
  • the second embodiment of the invention specified in the subclaims does not require drilling in the cylinder head for the supply and discharge lines, since they are made in one piece with a part of a cooling ring, so that they are cast into the cylinder head.
  • the cooling ring surrounding the valve seat ring is constructed from two cooling ring parts which are welded together. This ensures that the ring channel running in the cooling ring is oil-tight. This is particularly advantageous since no oil can get into the combustion chamber or the exhaust duct. Furthermore, there is no leakage oil if the valve seat ring has to be replaced or reworked.
  • the valve seat ring can be easily replaced and a free choice of materials for the valve seat ring is possible regardless of the cooling ring.
  • the surface of the ring channel is enlarged by at least two circumferential projections, so that an optimal heat transfer takes place.
  • Fig. 1 shows a cylinder head 1 with a camshaft housing 2 mounted thereon of an internal combustion engine operating in the four-stroke process.
  • the cylinder head 1 has, inter alia, at least one exhaust port 4 , to which an unillustrated valve is assigned.
  • a valve seat ring 5 which is surrounded by an annular channel 6 , is arranged in each outlet channel 4 .
  • the lubricating oil used to lubricate the internal combustion engine circulates as the cooling medium.
  • the ring channel 6 is provided with a feed line 7 and a discharge line 8 , which open into the ring channel 6 in two closely spaced openings 9 , 10 .
  • an oil channel 12 runs parallel to at least one camshaft 11 and supplies the camshaft bearings with lubricating oil.
  • the feed line 7 is formed by two bores 13 , 14 in the camshaft housing 2 which extend transversely to the oil channel 12 and a bore 15 in the cylinder head 1 which adjoins the bore 14 .
  • the oil pumped with pressure by an oil pump through the lubricating oil circuit of the internal combustion engine flows through the oil channel 12 and from there, inter alia, through the supply line 7 into the ring channel 6 .
  • the opening 9 is almost completely separated from the opening 10 by a projection 16 projecting into the annular channel 6 in both embodiments of the invention.
  • the outer surface 17 of the valve seat ring 5 and the outer surface 30 of the inner cooling ring part 23 are provided with at least two circumferential projections 18 .
  • the discharge line 8 in the camshaft housing 2 is connected to a cuboid collecting space 20 which has at least two outlet openings 21 .
  • the distance between the outlet openings 21 is selected so that the oil emerging from the collecting space 20 is sprayed directly onto the cams 22 of the camshaft 11 . This reduces the wear between cam 22 and the valves and increases their service life.
  • the oil has no direct contact with the valve seat ring 5 ' , but flows in an annular channel 6 which extends within a cooling ring 25 .
  • the cooling ring 25 consists of an inner cooling ring part 23 and an outer cooling ring part 24 .
  • the valve seat ring 5 ' has an L-shaped cross-sectional area and is pressed into the cooling ring 25 .
  • one leg 26 of the valve seat ring 5 ' is in surface contact with the inner surface 27 of the inner cooling ring part 23 and thus ensures good heat transfer from the valve seat ring 5' to the cooling ring 25 .
  • Another leg 28 bears against the end face 29 of the inner cooling ring part 23 facing the combustion chamber 3 and thus defines the desired pressing depth of the valve seat ring 5 ' into the cooling ring 25 . Furthermore, the displacement of the valve seat ring into the outlet channel 4 is prevented by the closing outlet valve.
  • the part of the supply line 7 running inside the cylinder head 1 and the discharge line 8 are made in one piece with the outer cooling ring part 24 . After welding the inner and outer cooling ring part 23, 24 to the cooling ring 25 , this is poured into the cylinder head 1 . Drilling for coolant supply and removal in the cylinder head 1 is thus eliminated.
  • the coolant supply within the camshaft housing 2 and the use of the discharged coolant as a lubricant between the cams 22 and valves is carried out in the same way as in the first embodiment of the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

Die Ventilsitzringe einer Viertakt-Brennkraftmaschine werden durch das Schmieröl des Ölkreislaufs gekühlt. Ein im Nockenwellengehäuse verlaufender Ölkanal wird so angebohrt, daß das Schmieröl vom Ölkanal in einen den Ventilsitzring umgebenden Ringkanal strömt. Durch einen den Ringkanal verschließenden Vorsprung wird eine Zwangsumströmung des Ventilsitzringes erzielt, bevor das Schmieröl durch eine nahe am Schmieröleintritt liegende Öffnung aus dem Ringkanal austritt. Vom Ringkanal strömt das Schmieröl durch eine Abführleitung zur Nockenwelle, wo es auf die Nocken verspritzt wird.The valve seat rings of a four-stroke internal combustion engine are cooled by the lubricating oil of the oil circuit. An oil channel running in the camshaft housing is drilled in such a way that the lubricating oil flows from the oil channel into an annular channel surrounding the valve seat ring. A positive flow around the valve seat ring is achieved by means of a projection which closes the annular channel before the lubricating oil emerges from the annular channel through an opening located close to the lubricating oil inlet. The lubricating oil flows from the ring channel through a discharge line to the camshaft, where it is sprayed onto the cams.

Description

Die Erfindung betrifft eine Ventilsitzringkühlung nach dem Oberbegriff des Anspruchs 1.The invention relates to a valve seat ring cooling system according to the preamble of claim 1.

Es ist bekannt, Ventilsitze, insbesondere die thermisch hochbelasteten Ventilsitzringe von Auslaßventilen einer Brennkraftmaschine zu kühlen. Aus der DE-PS 34 12 052 ist eine Ventilsitzringkühlung bekannt, bei der als Kühlmedium das der Brennkraftmaschinenkühlung dienende Kühlwasser verwendet wird. Dabei strömt das Kühlwasser radial in die Kühlkanäle der Ventilsitzringe ein und durch eine dem Eintritt gegenüberliegende Öffnung ab. Die Abflußöffnungen münden in einen Kanal, der direkt in die Saugseite der Kühlwasserpumpe führt, die die Brennkraftmaschine mit Kühlwasser versorgt.
Diese Anordnung ist nicht anwendbar, wenn die Brennkraftmaschine luftgekühlt ist.It is known to cool valve seats, in particular the thermally highly loaded valve seat rings of exhaust valves of an internal combustion engine. From DE-PS 34 12 052 a valve seat ring cooling is known in which the cooling water used for cooling the internal combustion engine is used as the cooling medium. The cooling water flows radially into the cooling channels of the valve seat rings and out through an opening opposite the inlet. The drain openings open into a channel that leads directly into the suction side of the cooling water pump, which supplies the internal combustion engine with cooling water.
This arrangement is not applicable when the internal combustion engine is air-cooled.

Die Ventilsitzringe einer flüssigkeitsgekühlten Brennkraftmaschine unabhängig vom Hauptkühlkreislauf durch ein anderes Kühlmittel, beispielsweise Schmieröl, in einem eigenen Kühlkreislauf zu kühlen, ist bekannt aus DE-05 15 76 727. Bei dieser Ausführung strömt das Kühlmittel zunächst zu den Auslaßventilsitzringen und von dort zu den Sitzringen der Einlaßventile.
Eine gleichmäßige Umströmung der Sitzringe ist aufgrund der Leitungsführung nicht gewährleistet. Zudem ist bei Verwendung von Schmieröl zur Ventilsitzringkühlung in dieser Erfindung ein separater Kühlmittelkreislauf mit einer eigenen Pumpe erforderlich.Cooling the valve seat rings of a liquid-cooled internal combustion engine independently of the main cooling circuit by another coolant, for example lubricating oil, in a separate cooling circuit is known from DE-05 15 76 727. In this embodiment, the coolant first flows to the outlet valve seat rings and from there to the seat rings Inlet valves.
A uniform flow around the seat rings is not guaranteed due to the piping. In addition, when using lubricating oil for valve seat ring cooling in this invention, a separate coolant circuit with its own pump is required.

Aufgabe der vorliegenden Erfindung ist es daher, eine Kühlvorrichtung für Ventilsitzringe einer luftgekühlten Brennkraftmaschine zu schaffen, die an einen vorhandenen Schmierölkreislauf angeschlossen ist und durch die eine optimale und gleichmäßige Kühlung aller Ventilsitzringe erzielt wird.The object of the present invention is therefore to provide a cooling device for valve seat rings of an air-cooled internal combustion engine, which is connected to an existing lubricating oil circuit and through which an optimal and uniform cooling of all valve seat rings is achieved.

Erfindungsgemäß wird diese Aufgabe durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst. Weitere, die Erfindung vorteilhaft ausgestaltende Merkmale sind in den Unteransprüchen benannt.
Die bei Anwendung der erfindungsgemäßen Lehre erzielbaren Vorteile sind insbesondere darin zu sehen, daß durch die Art der Zu- und Abführung des Kühlmittels der gesamte, jedem Ventilsitzring zugeführte Kühlmittelstrom den Ventilsitzring umströmt und daß der Ventilsitzring durch den eng benachbarten Kühlmittelzu- und ablauf fast vollständig umströmt wird, was für einen maximalen Wärmeübergang und eine gleichmäßige Kühlung von entscheidender Bedeutung ist. Weiterhin wird vorteilhafter Weise für die Zu- und Abfuhr des Kühlmittels ein vorhandener Kreislauf genutzt, dessen in ihm zirkulierendes Schmieröl als Kühlmittel benutzt wird. Das von den Ventilsitzringen zurückgeführte Schmieröl strömt nicht ungenutzt in den Ölsumpf, sondern wird auf die Nocken der Nockenwelle verspritzt. Dadurch sinkt der Verschleiß in der Reibpaarung Nocken/Ventil und die Lebensdauer beider Teile wird erhöht.
In einer ersten Ausführung der Erfindung sind die Zu- und Abführleitungen als Bohrungen senkrecht zur Trennfläche zwischen Zylinderkopf und Nockenwellengehäuse leicht herstellbar.
Die in den Unteransprüchen benannte zweite Ausführung der Erfindung erfordert keine Bohrbearbeitung im Zylinderkopf für die Zu- und Abführleitungen, da sie einteilig mit einem Teil eines Kühlrings ausgeführt sind, so daß diese mit in den Zylinderkopf eingegossen werden. Der den Ventilsitzring umgebende Kühlring ist aus zwei Kühlringteilen aufgebaut, die miteinander verschweißt werden. Somit ist sichergestellt, daß der im Kühlring verlaufende Ringkanal öldicht abgeschlossen ist. Dieses ist von besonderem Vorteil, da keinerlei Öl in den Brennraum bzw. den Auslaßkanal gelangen kann. Weiterhin tritt kein Lecköl aus, wenn der Ventilsitzring ausgewechselt oder nachgearbeitet werden muß. Der Ventilsitzring kann leicht ausgewechselt werden und eine freie Werkstoffwahl für den Ventilsitzring unabhängig vom Kühlring ist möglich.According to the invention, this object is achieved by the characterizing features of claim 1. Further features which advantageously design the invention are specified in the subclaims.
The advantages that can be achieved when applying the teaching according to the invention are to be seen in particular in that the type of supply and discharge of the coolant flows around the entire coolant flow supplied to each valve seat ring and that the valve seat ring flows almost completely through the closely adjacent coolant inlet and outlet becomes what is crucial for maximum heat transfer and uniform cooling. Furthermore, an existing circuit is advantageously used for the supply and removal of the coolant, the lubricating oil circulating in it is used as the coolant. The lubricating oil returned from the valve seat rings does not flow unused into the oil sump, but is sprayed onto the cams of the camshaft. This reduces wear in the cam / valve friction pair and increases the service life of both parts.
In a first embodiment of the invention, the feed and discharge lines can be easily produced as bores perpendicular to the separating surface between the cylinder head and the camshaft housing.
The second embodiment of the invention specified in the subclaims does not require drilling in the cylinder head for the supply and discharge lines, since they are made in one piece with a part of a cooling ring, so that they are cast into the cylinder head. The cooling ring surrounding the valve seat ring is constructed from two cooling ring parts which are welded together. This ensures that the ring channel running in the cooling ring is oil-tight. This is particularly advantageous since no oil can get into the combustion chamber or the exhaust duct. Furthermore, there is no leakage oil if the valve seat ring has to be replaced or reworked. The valve seat ring can be easily replaced and a free choice of materials for the valve seat ring is possible regardless of the cooling ring.

In beiden Ausführungen der Erfindung ist die Oberfläche des Ringkanales durch mindestens zwei umlaufende Vorsprünge vergrößert, so daß ein optimaler Wärmeübergang stattfindet.In both embodiments of the invention, the surface of the ring channel is enlarged by at least two circumferential projections, so that an optimal heat transfer takes place.

Die nachfolgend aufgeführten Figuren erläutern die Erfindung näher.The figures listed below explain the invention in more detail.

Es zeigt:

  • Fig. 1 eine erste Ausführung der Erfindung in einem Zylinderkopf angeordnet im Schnitt,
  • Fig. 2 einen Schnitt aus Fig. 1 entlang der Linie II-II,
  • Fig. 3 ein Detail aus Fig. 1 in einer Draufsicht,
  • Fig. 4 eine zweite Ausführung der Erfindung in einem Zylinderkopf angeordnet im Schnitt,
  • Fig. 5 eine Einzelheit X aus Fig. 4.
It shows:
  • 1 shows a first embodiment of the invention in a cylinder head arranged in section,
  • 2 shows a section from FIG. 1 along the line II-II,
  • 3 shows a detail from FIG. 1 in a top view,
  • 4 shows a second embodiment of the invention arranged in a cylinder head in section,
  • 5 shows a detail X from FIG. 4.

Fig. 1 zeigt einen Zylinderkopf 1 mit einem darauf montierten Nockenwellen­gehäuse 2 einer im Viertakt-Verfahren arbeitenden Brennkraftmaschine. Zur Steuerung des Gaswechsels in einem Brennraum 3 weist der Zylinderkopf 1 u.a. mindestens einen Auslaßkanal 4 auf, dem ein nicht gezeichnetes Ventil zugeordnet ist. In jedem Auslaßkanal 4 ist ein Ventilsitzring 5 angeordnet, der von einem Ringkanal 6 umgeben ist. In diesem zirkuliert als Kühlmedium das zur Brennkraftmaschinenschmierung dienende Schmieröl. Hierzu ist der Ringkanal 6 mit einer Zufuhrleitung 7 und einer Abführleitung 8 versehen, die in zwei dicht zusammenliegenden Öffnungen 9, 10 in den Ringkanal 6 münden.
Im Nockenwellengehäuse 2 verläuft parallel zu mindestens einer Nockenwelle 11 ein Ölkanal 12, der die Nockenwellenlager mit Schmieröl versorgt. Durch zwei im Nockenwellengehäuse 2 quer zum Ölkanal 12 verlaufende Bohrungen 13, 14 und eine sich an die Bohrung 14 anschließende Bohrung 15 im Zylinderkopf 1 wird die Zufuhrleitung 7 gebildet.
Das mit Druck von einer Ölpumpe durch den Schmierölkreislauf der Brennkraftmaschine geförderte Öl strömt durch den Ölkanal 12 und von dort u.a. durch die Zufuhrleitung 7 in den Ringkanal 6. Durch einen in beiden Ausführungen der Erfindung in den Ringkanal 6 ragenden Vorsprung 16 wird die Öffnung 9 nahezu vollstandig von der Öffnung 10 getrennt. Somit strömt nur ein sehr geringer Teil der Ölmenge durch einen Kurzschluß direkt von der Öffnung 9 zur Öffnung 10. Um einen optimalen Wärmeübergang zwischen dem durch die Abgase der Brennkraftmaschine stark erhitzten Ventilsitzring 5, 5′ und dem Öl zu erzielen, ist die Außenfläche 17 des Ventilsitzrings 5 und die Außenfläche 30 des inneren Kühlringteils 23 mit mindestens zwei umlaufenden Vorsprüngen 18 versehen.Fig. 1 shows a cylinder head 1 with a camshaft housing 2 mounted thereon of an internal combustion engine operating in the four-stroke process. To control the gas exchange in a combustion chamber 3 , the cylinder head 1 has, inter alia, at least one exhaust port 4 , to which an unillustrated valve is assigned. A valve seat ring 5 , which is surrounded by an annular channel 6 , is arranged in each outlet channel 4 . The lubricating oil used to lubricate the internal combustion engine circulates as the cooling medium. For this purpose, the ring channel 6 is provided with a feed line 7 and a discharge line 8 , which open into the ring channel 6 in two closely spaced openings 9 , 10 .
In the camshaft housing 2 , an oil channel 12 runs parallel to at least one camshaft 11 and supplies the camshaft bearings with lubricating oil. The feed line 7 is formed by two bores 13 , 14 in the camshaft housing 2 which extend transversely to the oil channel 12 and a bore 15 in the cylinder head 1 which adjoins the bore 14 .
The oil pumped with pressure by an oil pump through the lubricating oil circuit of the internal combustion engine flows through the oil channel 12 and from there, inter alia, through the supply line 7 into the ring channel 6 . The opening 9 is almost completely separated from the opening 10 by a projection 16 projecting into the annular channel 6 in both embodiments of the invention. Thus, only a very small part of the oil quantity flows directly from opening 9 to opening 10 through a short circuit. In order to achieve optimum heat transfer between the valve seat ring 5, 5 ' , which is strongly heated by the exhaust gases of the internal combustion engine , and the oil, the outer surface 17 of the valve seat ring 5 and the outer surface 30 of the inner cooling ring part 23 are provided with at least two circumferential projections 18 .

Nachdem das Öl den Ventilsitzring 5 fast vollstandig umströmt hat, tritt es durch die Öffnung 10 in die Abführleitung 8. Diese wird durch eine Bohrung 19 gebildet, die senkrecht zur Trennfläche zwischen Zylinderkopf 1 und Nockenwellengehäuse 2 verläuft und vom Ringkanal 5 auf die Nockenwelle 11 weist.
Aus Fig. 3 ist ersichtlich, daß die Abführleitung 8 im Nockenwellengehäuse 2 an einen quaderförmigen Sammelraum 20 angeschlossen ist, der mindestens zwei Austrittsöffnungen 21 aufweist. Der Abstand der Austrittsöffnungen 21 zueinander ist so gewählt, daß das aus dem Sammelraum 20 austretende Öl direkt auf die Nocken 22 der Nockenwelle 11 verspritzt wird. Dadurch wird der Verschleiß zwischen Nocken 22 und den Ventilen herabgesetzt und ihre Lebensdauer erhöht.
Fig. 4 zeigt eine zweite Ausführung der Erfindung. Hierbei hat das Öl keinen unmittelbaren Kontakt mit dem Ventilsitzring 5′, sondern strömt in einem Ringkanal 6, der innerhalb eines Kühlringes 25 verläuft. Der Kühlring 25 besteht aus einem inneren Kühlringteil 23 und einem äußeren Kühlringteil 24. Der Ventilsitzring 5′ weist eine L-förmige Querschnittsfläche auf und ist in den Kühlring 25 eingepreßt. Dabei steht ein Schenkel 26 des Ventilsitzringes 5′ in Flächenkontakt mit der Innenfläche 27 des inneren Kühlringteils 23 und gewährleistet so einen guten Wärmeübergang vom Ventilsitzring 5′ auf den Kühlring 25. Ein weiterer Schenkel 28 liegt an der dem Brennraum 3 zugewandten Stirnfläche 29 des inneren Kühlringteils 23 an und definiert so die gewünschte Einpreßtiefe des Ventilsitzringes 5′ in den Kühlring 25. Weiterhin ist so das Verschieben des Ventilsitzringes in den Auslaßkanal 4 durch das schließende Auslaßventil verhindert.
Der innerhalb des Zylinderkopfes 1 verlaufende Teil der Zufuhrleitung 7 sowie die Abführleitung 8 sind einteilig mit dem äußeren Kühlringteil 24 ausgeführt. Nach dem Verschweißen von innerem und äußerem Kühlringteil 23, 24 zum Kühlring 25 wird dieser in den Zylinderkopf 1 eingegossen. Die Bohrbearbeitung für Kühlmittelzu- und -abfuhr im Zylinderkopf 1 entfällt somit. Die Kühlmittelzufuhr innerhalb des Nockenwellengehäuses 2 und die Verwendung des abgeführten Kühlmittels als Schmiermittel zwischen Nocken 22 und Ventilen ist in gleicher Weise ausgeführt wie bei der ersten Ausführung der Erfindung.After the oil has almost completely flowed around the valve seat ring 5 , it passes through the opening 10 into the discharge line 8 . This is formed by a bore 19 which runs perpendicular to the separating surface between the cylinder head 1 and the camshaft housing 2 and points from the annular channel 5 to the camshaft 11 .
From Fig. 3 it can be seen that the discharge line 8 in the camshaft housing 2 is connected to a cuboid collecting space 20 which has at least two outlet openings 21 . The distance between the outlet openings 21 is selected so that the oil emerging from the collecting space 20 is sprayed directly onto the cams 22 of the camshaft 11 . This reduces the wear between cam 22 and the valves and increases their service life.
Fig. 4 shows a second embodiment of the invention. Here, the oil has no direct contact with the valve seat ring 5 ' , but flows in an annular channel 6 which extends within a cooling ring 25 . The cooling ring 25 consists of an inner cooling ring part 23 and an outer cooling ring part 24 . The valve seat ring 5 ' has an L-shaped cross-sectional area and is pressed into the cooling ring 25 . Here, one leg 26 of the valve seat ring 5 'is in surface contact with the inner surface 27 of the inner cooling ring part 23 and thus ensures good heat transfer from the valve seat ring 5' to the cooling ring 25 . Another leg 28 bears against the end face 29 of the inner cooling ring part 23 facing the combustion chamber 3 and thus defines the desired pressing depth of the valve seat ring 5 ' into the cooling ring 25 . Furthermore, the displacement of the valve seat ring into the outlet channel 4 is prevented by the closing outlet valve.
The part of the supply line 7 running inside the cylinder head 1 and the discharge line 8 are made in one piece with the outer cooling ring part 24 . After welding the inner and outer cooling ring part 23, 24 to the cooling ring 25 , this is poured into the cylinder head 1 . Drilling for coolant supply and removal in the cylinder head 1 is thus eliminated. The coolant supply within the camshaft housing 2 and the use of the discharged coolant as a lubricant between the cams 22 and valves is carried out in the same way as in the first embodiment of the invention.

Claims (10)

1. Kühlvorrichtung für die im Zylinderkopf einer luftgekühlten Brennkraftmaschine angeordneten Ventilsitzringe, mit jeweils einem von Schmieröl durchströmten, die Ventilsitzringe umgebenden Ringkanal und mit einem weiteren Ölkanal, der die Lagerstellen einer Nockenwelle mit Schmieröl versorgt und in einem oberhalb eines Zylinderkopfes angeordneten Nockenwellengehäuse parallel zur Nockenwelle verläuft, und mit jeweils einer Zuführleitung, die vom Ölkanal zu dem Ringkanal führt, sowie einer Abführleitung, die vom Ringkanal in das Nockenwellengehäuse führt, dadurch gekennzeichnet, daß je eine Zu- und Abführleitung (7, 8) in eng benachbarten Öffnungen (9, 10) in jeden Ringkanal (6) münden und daß eine Austrittsöffnung (21) der Abführleitung (8) im Nockenwellengehäuse (2) in unmittelbarer Nähe von Nocken (22) angeordnet ist, und daß der Ringkanal (6) zwischen den beiden Öffnungen (9, 10) einen ihn stark einengenden Vorsprung (16) aufweist.1.Cooling device for the valve seat rings arranged in the cylinder head of an air-cooled internal combustion engine, each with an annular channel through which lubricating oil flows and surrounding the valve seat rings and with a further oil channel which supplies the bearing points of a camshaft with lubricating oil and runs parallel to the camshaft in a camshaft housing arranged above a cylinder head , and each with a feed line that leads from the oil channel to the ring channel, and a discharge line that leads from the ring channel into the camshaft housing, characterized in that a feed and discharge line (7, 8) each in closely adjacent openings (9, 10 ) open into each ring channel (6) and that an outlet opening (21) of the discharge line (8) is arranged in the camshaft housing ( 2) in the immediate vicinity of cams (22) , and that the ring channel (6) between the two openings (9, 10) has a protruding projection (16) . 2. Kühlvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Ringkanal (6) in einem Kühlring (25) ausgebildet ist, der den Ventilsitzring (5) umschließt.2. Cooling device according to claim 1, characterized in that the annular channel (6) is formed in a cooling ring (25) which surrounds the valve seat ring (5) . 3. Kühlvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Kühlring (25) aus einem inneren Kühlringteil (23) und einem äußeren Kühlringteil (24) besteht, und daß das äußere Kühlringteil (24) eine Zu- und Abführleitung (7, 8) aufweist, wobei diese in eng benachbarten Öffnungen (9, 10) in das äußere Kühlringteil (24) münden.3. Cooling device according to claim 2, characterized in that the cooling ring (25) consists of an inner cooling ring part (23) and an outer cooling ring part (24) , and that the outer cooling ring part (24) has a supply and discharge line (7, 8) having open openings (9, 10) in the outer cooling ring part (24) . 4. Kühlvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß das äußere Kühlringteil (23) einteilig mit der Zu- und Abführleitung (7, 8) ausgebildet ist.4. Cooling device according to claim 3, characterized in that the outer cooling ring part (23) is integrally formed with the supply and discharge line (7, 8) . 5. Kühlvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß jede Zufuhrleitung (7) durch quer zum Ölkanal (12) im Nockenwellengehäuse (2) und in einem Zylinderkopf (1) verlaufende Bohrungen (13, 14, 15) gebildet ist und daß die Abführleitung (8) durch je eine Bohrung (19) im Zylinderkopf (1) gebildet ist, deren Richtung vom Ringkanal (6) senkrecht auf die Nockenwellenmittellängsachse (M) weist.5. Cooling device according to claim 1, characterized in that each supply line (7) through transverse to the oil channel (12) in the camshaft housing (2) and in a cylinder head (1) bores (13, 14, 15) is formed and that the discharge line (8) is formed by a bore (19) in the cylinder head (1) , the direction of which from the ring channel (6) points perpendicular to the central longitudinal axis of the camshaft (M) . 6. Kühlvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß jeder Abführleitung (8) in der Trennfläche zwischen Zylinderkopf (1) und Nockenwellengehäuse (2) ein Sammelraum (20) zugeordnet ist, der im Nockenwellengehäuse (2) ausgebildet ist und mindestens zwei Austrittsöffnungen (21) zur Nockenwelle (11) hin aufweist.6. Cooling device according to claim 1 or 2, characterized in that each discharge line (8) in the interface between the cylinder head (1) and the camshaft housing ( 2) is assigned a collecting space (20) which is formed in the camshaft housing (2) and at least two Has outlet openings (21) to the camshaft (11) . 7. Kühlvorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß jede Austrittsöffnung (21) eines Sammelraumes (20) auf einen Nocken (22) der Nockenwelle (11) weist.7. Cooling device according to claim 6, characterized in that each outlet opening (21) of a collecting space (20) has a cam (22) of the camshaft (11) . 8. Kühlvorrichtung nach Anspruch 1 und 2, dadurch gekennzeichnet, daß die Außenfläche (17) des Ventilsitzringes (5) und die Außenfläche (30) des inneren Kühlringteils (23) mindestens zwei umlaufende Vorsprünge (18) aufweisen.8. Cooling device according to claim 1 and 2, characterized in that the outer surface (17) of the valve seat ring (5) and the outer surface (30) of the inner cooling ring part (23) have at least two circumferential projections (18) . 9. Kühlvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß jeder Ventilsitzring (5′) einen L-förmigen Querschnitt aufweist und mit einem Schenkel (26) an der Innenfläche (27) des inneren Kühlringteils (23) anliegt und mit einem Schenkel (28) an einer Stirnfläche (29) des inneren Kühlringteils (23) anliegt.9. Cooling device according to claim 2, characterized in that each valve seat ring (5 ') has an L-shaped cross section and rests with a leg (26) on the inner surface (27) of the inner cooling ring part (23) and with a leg (28) abuts an end face (29) of the inner cooling ring part (23) . 10.Kühlvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß als Werkstoff für den Kühlring (25) Buntmetall oder Stahl verwendet wird.10. Cooling device according to claim 2, characterized in that non-ferrous metal or steel is used as the material for the cooling ring (25) .
EP89111053A 1988-08-30 1989-06-19 Cooling system for the valve seats in the cylinder head of an internal-combustion engine Expired - Lifetime EP0356641B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3829339 1988-08-30
DE3829339A DE3829339C1 (en) 1988-08-30 1988-08-30

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EP0356641A2 true EP0356641A2 (en) 1990-03-07
EP0356641A3 EP0356641A3 (en) 1990-05-23
EP0356641B1 EP0356641B1 (en) 1992-10-07

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EP89111053A Expired - Lifetime EP0356641B1 (en) 1988-08-30 1989-06-19 Cooling system for the valve seats in the cylinder head of an internal-combustion engine

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US (1) US4941436A (en)
EP (1) EP0356641B1 (en)
JP (1) JPH02104908A (en)
DE (2) DE3829339C1 (en)

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CN102135048A (en) * 2010-01-26 2011-07-27 航空机动化公司 Internal combustion engine cylinder cover with cooling circuit
DE102014012807A1 (en) 2014-08-28 2016-03-03 Daimler Ag Cylinder head for an internal combustion engine, in particular a motor vehicle

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AT404390B (en) * 1992-09-24 1998-11-25 Avl Verbrennungskraft Messtech INTERNAL COMBUSTION ENGINE WITH A CHILLED VALVE SEAT RING
KR19990001641A (en) * 1997-06-17 1999-01-15 김영귀 Cooling device of car intake / exhaust valve seat
DE10122581A1 (en) * 2001-05-10 2003-01-09 Mahle Ventiltrieb Gmbh Cooled valve seat ring
DE102004027084A1 (en) * 2004-06-02 2005-12-29 Man B & W Diesel Ag Cooled valve seat ring for a cylinder head of an I.C. engine comprises ring parts forming an annular flow channel which is integrated via inlet and outlet holes in one of the ring parts after pressing into the cylinder head
FR2876747A1 (en) * 2004-10-15 2006-04-21 Renault Sas Heat engine for motor vehicle, has electrical heating unit with coil around seat of inlet valve in head and traversed by direct current for heating seat and valve to reheat inlet gas traversing inlet pipe activated before starting of engine
FI124071B (en) * 2006-11-14 2014-02-28 Waertsilae Finland Oy Piston engine valve seat ring
FR3013771A1 (en) * 2013-11-22 2015-05-29 Peugeot Citroen Automobiles Sa THERMAL ENGINE OF A MOTOR VEHICLE HAVING AN INSERT FOR THE CIRCULATION OF A FLUID AND CORRESPONDING INSERT
JP2018048587A (en) * 2016-09-21 2018-03-29 トヨタ自動車株式会社 Internal combustion engine
WO2018156682A1 (en) 2017-02-24 2018-08-30 Cummins Inc. Engine cooling system including cooled exhaust seats
US10989146B2 (en) * 2018-11-05 2021-04-27 Caterpillar Inc. Oil injection methods for combustion enhancement in natural gas reciprocating engines

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CN102135048A (en) * 2010-01-26 2011-07-27 航空机动化公司 Internal combustion engine cylinder cover with cooling circuit
CN102135048B (en) * 2010-01-26 2015-09-30 航空机动化公司 Comprise the cylinder head of the internal-combustion engine of cooling circuit
DE102014012807A1 (en) 2014-08-28 2016-03-03 Daimler Ag Cylinder head for an internal combustion engine, in particular a motor vehicle

Also Published As

Publication number Publication date
DE3829339C1 (en) 1989-12-14
JPH02104908A (en) 1990-04-17
US4941436A (en) 1990-07-17
EP0356641A3 (en) 1990-05-23
DE58902410D1 (en) 1992-11-12
EP0356641B1 (en) 1992-10-07

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