EP0282808B1 - Cylinder heads for v-type internal-combustion engines - Google Patents

Cylinder heads for v-type internal-combustion engines Download PDF

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Publication number
EP0282808B1
EP0282808B1 EP88103084A EP88103084A EP0282808B1 EP 0282808 B1 EP0282808 B1 EP 0282808B1 EP 88103084 A EP88103084 A EP 88103084A EP 88103084 A EP88103084 A EP 88103084A EP 0282808 B1 EP0282808 B1 EP 0282808B1
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EP
European Patent Office
Prior art keywords
longitudinal
coolant
cylinder
ducts
cylinder head
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP88103084A
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German (de)
French (fr)
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EP0282808A3 (en
EP0282808A2 (en
Inventor
Jiri Seidl
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication of EP0282808A3 publication Critical patent/EP0282808A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0012—Crankcases of V-engines
    • 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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • 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
    • F02F1/26—Cylinder heads having cooling means
    • F02F1/36—Cylinder heads having cooling means for liquid cooling
    • F02F1/40—Cylinder heads having cooling means for liquid cooling cylinder heads with means for directing, guiding, or distributing liquid stream 
    • 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • 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
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • 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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1824—Number of cylinders six
    • 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 directed to a unit cylinder head for liquid-cooled internal combustion engine with opposing cylinder housings is based on the preamble of claim 1 from US-A-1,629,664.
  • the coolant is fed from a pump to the cooling jacket of the cylinder housing via a distributor line arranged on the outside thereof.
  • the coolant is fed through openings in the top wall of the cylinder housing both to the coolant chamber and directly to the longitudinal channel of the respective unit cylinder head.
  • This is essentially designed as a cylinder head cover by the V-motor controlled below, the longitudinal channel integrated in the cover in the area of all gas exchange devices being connected to the coolant chamber through which it flows over almost its entire longitudinal extent.
  • This unit cylinder head which was created especially for V-engines, provides a coolant flow system with an unfavorable temperature distribution.
  • the invention has for its object to improve the coolant flow in the generic unit cylinder heads with a view to a favorable temperature distribution, but without increasing the length of the unit cylinder heads in excess of the machine length determined essentially by the end reference planes of the machine housing.
  • Claim 2 describes an advantageous embodiment of the invention for a unit cylinder head designed according to the cross-flow principle.
  • the cross-flow through the cylinder heads is preferred for a V-engine with high power.
  • these cylinder heads can be designed in a known manner with more than two intake ports per combustion chamber or per cylinder.
  • the large number of inlet channels per cylinder results in interconnected walls of the inlet channels at small cylinder distances.
  • these interconnected walls essentially separate them from the respective coolant chamber. These walls thus form a partial delimitation of the longitudinal channels, which further feed the coolant emerging from the cylinder heads at high temperature to a supply or collecting line.
  • the structurally integrated longitudinal channels of the coolant flow system thus serve
  • an advantageous temperature distribution in the cylinder heads between their exhaust and intake sides which would be relatively cool without this measure due to the many intake ports per cylinder compared to the exhaust sides with the disadvantageous consequence of unfavorable material stresses.
  • the walls can finally be designed for the safe discharge of gas and vapor bubbles from the coolant spaces with openings of small cross-section to the longitudinal channels.
  • the unit cylinder head described so far has a coolant flow system with oppositely directed longitudinal flows through its design according to the invention.
  • a transverse flow overlying the longitudinal flow of the coolant chamber to the outlet channels is achieved.
  • the strength of the cross flow can be advantageously combined with the longitudinal flow through the selection of appropriate cross sections. This measure allows the temperature distribution in the unit cylinder head to be advantageously controlled, in particular when the V engine has a high power output on the exhaust side.
  • Claim 4 describes in the first characteristic feature an embodiment for a first example of a line arrangement with a collecting line arranged on half the machine length for a heat exchanger flow.
  • the longitudinal channels extended beyond the connections of the manifold to the end regions of the unit cylinder heads remote from the transverse channels advantageously serve for further line connections described in the second characterizing feature of claim 4. So that can shorter lines can be achieved for the separate parts of the short-circuit line and the heating flow.
  • claim 5 describes a further example of a line arrangement with a collecting line arranged on the end face of the internal combustion engine between the line channels, which is connected on the one hand to a short-circuit line and on the other hand to a heat exchanger flow.
  • a liquid-cooled internal combustion engine 10 with cylinder housings 11 in a V arrangement has, as can be seen in more detail in FIG. 2, cylinder rows 12 arranged in mutual offset “x”.
  • Cylinder heads 13 of the internal combustion engine or V-engine 10 have, as can be seen from FIGS. 2 and 3, inlet channels 15 arranged in opposite longitudinal sides 14, while the longitudinal sides 14 Lhack of the cylinder heads 13 facing away from V-space 16 are assigned to 13 outlet channels 17 .
  • Each cylinder head 13 has a coolant chamber 18 between the inlet channels 15 and the outlet channels 17. Furthermore, the cylinder heads 13 are equipped on their longitudinal sides 14 facing the V space 16 with longitudinal channels 19, which are structurally integrated in the cylinder heads 13. The longitudinal channels 19 have connections 20 arranged approximately half the length of the machine for a manifold 21 of a heat exchanger feed line 22 to a coolant heat exchanger 23.
  • the longitudinal channels 19 each have a further line connection 24 in the end regions of the cylinder heads 13, the line connection 24 of the longitudinal channel 19 of the cylinder head 13 on the left in FIG. 2 serving for a short-circuit line 25, while the line connection 24 of the longitudinal channel 19 of the right cylinder head 13 is one Heating flow 26 is used.
  • the further line connection 24 arranged in dashed lines in the right cylinder head 13 is closed by a blind plug.
  • the short-circuit line 25 is connected via a return thermostat 27 to a coolant delivery pump 29 arranged on the front side of the V-engine 10.
  • the longitudinal channels 19 are connected to the coolant spaces 18 in the other opposite end regions of the cylinder heads 13 via transverse channels 30.
  • Each transverse channel 30 is arranged on the cylinder head 13 in the end region of the respective cylinder housing 11 with the cylinder row 12 which is at a maximum distance from an end reference plane 31 or 32 due to the offset “x”. With this arrangement, the overall length of each cylinder head 13 remains in the machine length determined by the two end reference planes 31 and 32.
  • the transverse channels 30 are connected to the coolant spaces 18 of the cylinder heads 13 via the outlet channels 17 arranged adjacent drain lines 33. This is one for V-engines 10 with high performance preferred cross flow of the cylinder heads 13 achieved.
  • each cylinder of the respective cylinder bank 12 in the cylinder head is assigned three inlet channels 15.
  • the walls 34 of all the inlet channels 15 of a cylinder head 13 are connected to one another and essentially separate the coolant chamber 18 from the structurally integrated longitudinal channel 19.
  • the walls 34 have openings 35 of small cross-section for the safe discharge of gas and vapor bubbles from the coolant chamber 18 in the longitudinal channel 19.
  • FIG. 4 shows an internal combustion engine 100 in which the connections for a manifold 210 are identical to line connections 240 of the longitudinal channels 190 arranged in the end regions of the cylinder heads 130.
  • the separate connections 20 of the longitudinal channels 190 are closed by blind plugs.
  • the manifold 210 is connected on the one hand to a short-circuit line 250 and on the other hand to a heat exchanger flow 220.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Description

Die auf einen Einheits-Zylinderkopf für flüssigkeitsgekühlte Brennkraftmaschine mit gegenüberliegenden Zylindergehäusen gerichtete Erfindung geht nach dem Oberbegriff des Patentanspruches 1 von der US-A-1,629,664 aus.The invention directed to a unit cylinder head for liquid-cooled internal combustion engine with opposing cylinder housings is based on the preamble of claim 1 from US-A-1,629,664.

Bei diesem bekannten V-Motor wird das Kühlmittel von einer Pumpe dem Kühlmantel des Zylindergehäuses über eine an diesem außen angeordnete Verteilerleitung zugeführt. Über Durchbrechungen in der Deckwand des Zylindergehäuses ist das Kühlmittel sowohl dem Kühlmittelraum als auch direkt dem Längskanal des jeweiligen Einheits-Zylinderkopfes zugeführt. Dieser ist durch den unten gesteuerten V-Motor im wesentlichen als Zylinderkopf-Deckel gestaltet, wobei der im Deckel im Bereich sämtlicher Gaswechseleinrichtungen integrierte Längskanal über nahezu seine gesamte Längserstreckung mit dem quer durchströmten Kühlmittelraum in Verbindung steht. Mit diesem insbesondere für V-Motore geschaffenen Einheits-Zylinderkopf ist ein Kühlmittelfluß-System mit ungünstiger Temperaturverteilung gegeben.In this known V-type engine, the coolant is fed from a pump to the cooling jacket of the cylinder housing via a distributor line arranged on the outside thereof. The coolant is fed through openings in the top wall of the cylinder housing both to the coolant chamber and directly to the longitudinal channel of the respective unit cylinder head. This is essentially designed as a cylinder head cover by the V-motor controlled below, the longitudinal channel integrated in the cover in the area of all gas exchange devices being connected to the coolant chamber through which it flows over almost its entire longitudinal extent. This unit cylinder head, which was created especially for V-engines, provides a coolant flow system with an unfavorable temperature distribution.

Der Erfindung liegt die Aufgabe zugrunde, den Kühlmittelfluß in den gattungsgemäßen Einheits-Zylinderköpfen im Hinblick auf eine günstige Temperaturverteilung zu verbessern, jedoch ohne die Einheits-Zylinderköpfe in der Baulänge über die im wesentlichen durch die stirnseitigen Bezugsebenen des Maschinengehäuses bestimmte Maschinenlänge hinaus zu vergrößern.The invention has for its object to improve the coolant flow in the generic unit cylinder heads with a view to a favorable temperature distribution, but without increasing the length of the unit cylinder heads in excess of the machine length determined essentially by the end reference planes of the machine housing.

Diese Aufgabe wird durch die im Kennzeichen des Patentanspruches 1 angegebenen Merkmale gelöst. Mit dem nach der Erfindung gestalteten Einheits-Zylinderkopf ist ein Kühlmittelfluß-System mit einander entgegensetzt gerichteten Längsdurchströmungen im Zylinderkopf erreicht mit dem Vorteil einer günstigen Temperaturverteilung. Weiter wird die Ausgestaltung des Einheits-Zylinderkopfes durch die gezielte Ausnützung eines Zylinderreihen-Versatzes zur entsprechenden Anordnung des Querkanals gefördert. Damit entspricht weiter in vorteilhafter Weise die Baulänge des Einheits-Zylinderkopfes der durch die stirnseitigen Bezugsebenen bestimmten Länge des Maschinengehäuses, wobei die Bezugsebenen im wesentlichen durch die Stirnseiten der entweder gleichauf oder gemäß dem Zylinderreihen-Versatz unterschiedlich endenden Zylindergehäuse des V-Motors bestimmt sind.This object is achieved by the features specified in the characterizing part of patent claim 1. With the unit cylinder head designed according to the invention, a coolant flow system with oppositely directed longitudinal flows in the cylinder head is achieved with the advantage of a favorable temperature distribution. Furthermore, the design of the unit cylinder head is promoted by the targeted use of a cylinder row offset for the corresponding arrangement of the transverse channel. This further advantageously corresponds to the overall length of the unit cylinder head of the length of the machine housing determined by the end reference planes, the reference planes being essentially determined by the end sides of the cylinder housings of the V-engine, which end either in the same way or according to the cylinder row offset.

Eine vorteilhafte Ausgestaltung der Erfindung für einen nach dem Querstromprinzip gestalteten Einheits-Zylinderkopf beschreibt Anspruch 2. Die Querdurchströmung der Zylinderköpfe ist bevorzugt bei einem V-Motor mit hoher Leistung. Zur Erzielung einer hohen Leistung können diese Zylinderköpfe in bekannter Weise mit mehr als zwei Einlaßkanälen je Brennraum bzw. je Zylinder ausgebildet sein. Die große Anzahl an Einlaßkanälen je Zylinder ergibt bei geringen Zylinderabständen miteinander verbundene Wandungen der Einlaßkanäle. Diese miteinander verbundenen Wandungen trennen bei in den Einheits-Zylinderköpfen baulich integrierten Längskanälen diese im wesentlichen vom jeweiligen Kühlmittelraum. Diese Wandungen bilden somit eine Teilbegrenzung der Längskanäle, die das mit hoher Temperatur aus den Zylinderköpfen austretende Kühlmittel im weiteren einer Vorlauf- bzw. Sammelleitung zuführen. Damit dienen die baulich integrierten Längskanäle des Kühlmittelfluß-Systems zusätzlich einer vorteilhaften Temperaturverteilung in den Zylinderköpfen zwischen deren Auslaß- und Einlaßseiten, die ohne diese Maßnahme aufgrund der vielen Einlaßkanäle je Zylinder gegenüber den Auslaßseiten relativ kühl wären mit der nachteiligen Folge ungünstiger Werkstoffspannungen. Die Wandungen können schließlich zur sicheren Ableitung von Gas- und Dampf-Blasen aus den Kühlmittelräumen mit Durchbrechungen von kleinem Querschnitt zu den Längskanälen ausgebildet sein.Claim 2 describes an advantageous embodiment of the invention for a unit cylinder head designed according to the cross-flow principle. The cross-flow through the cylinder heads is preferred for a V-engine with high power. To achieve high performance, these cylinder heads can be designed in a known manner with more than two intake ports per combustion chamber or per cylinder. The large number of inlet channels per cylinder results in interconnected walls of the inlet channels at small cylinder distances. In the case of longitudinal channels which are structurally integrated in the unit cylinder heads, these interconnected walls essentially separate them from the respective coolant chamber. These walls thus form a partial delimitation of the longitudinal channels, which further feed the coolant emerging from the cylinder heads at high temperature to a supply or collecting line. The structurally integrated longitudinal channels of the coolant flow system thus serve In addition, an advantageous temperature distribution in the cylinder heads between their exhaust and intake sides, which would be relatively cool without this measure due to the many intake ports per cylinder compared to the exhaust sides with the disadvantageous consequence of unfavorable material stresses. The walls can finally be designed for the safe discharge of gas and vapor bubbles from the coolant spaces with openings of small cross-section to the longitudinal channels.

Der bisher beschriebene Einheits-Zylinderkopf weist durch seine erfindungsgemäße Gestaltung ein Kühlmittelfluß-System mit einander entgegengesetzt gerichteten Längsdurchströmungen auf. Mit der weiteren Ausgestaltung des Einheits-Zylinderkopfes nach Anspruch 3 mit einer den Auslaßkanälen benachbart angeordneten Ablaufleitung zur zusätzlichen Verbindung des Kühlmittelraumes mit dem Querkanal wird eine die Längsdurchströmung des Kühlmittelraumes überlagernde Querströmung zu den Auslaßkanälen erzielt. Die Stärke der Querströmung läßt sich mit der Längsdurchströmung durch die Wahl entsprechender Querschnitte vorteilhaft kombinieren. Durch diese Maßnahme kann die Temperaturverteilung im Einheits-Zylinderkopf insbesondere bei hoher Leistungsabgabe des V-Motors auf der Auslaßseite vorteilhaft gesteuert werden.The unit cylinder head described so far has a coolant flow system with oppositely directed longitudinal flows through its design according to the invention. With the further configuration of the unit cylinder head according to claim 3 with a discharge line arranged adjacent to the outlet channels for the additional connection of the coolant chamber to the transverse channel, a transverse flow overlying the longitudinal flow of the coolant chamber to the outlet channels is achieved. The strength of the cross flow can be advantageously combined with the longitudinal flow through the selection of appropriate cross sections. This measure allows the temperature distribution in the unit cylinder head to be advantageously controlled, in particular when the V engine has a high power output on the exhaust side.

Anspruch 4 beschreibt im ersten Kennzeichenmerkmal eine Ausgestaltung für ein erstes Beispiel einer Leitungsanordnung mit einer auf halber Maschinenlänge angeordneten Sammelleitung für einen Wärmetauscher-Vorlauf. Die über die Anschlüsse der Sammelleitung hinaus bis in die von den Querkanälen entfernten Endbereiche der Einheits-Zylinderköpfe verlängerten Längskanäle dienen vorteilhaft für weitere im zweiten Kennzeichenmerkmal des Anspruches 4 beschriebene Leitungsverbindungen. Damit können für die separaten Teile der Kurzschlußleitung und des Heizungsvorlaufes kürzere Leitungen erzielt werden.Claim 4 describes in the first characteristic feature an embodiment for a first example of a line arrangement with a collecting line arranged on half the machine length for a heat exchanger flow. The longitudinal channels extended beyond the connections of the manifold to the end regions of the unit cylinder heads remote from the transverse channels advantageously serve for further line connections described in the second characterizing feature of claim 4. So that can shorter lines can be achieved for the separate parts of the short-circuit line and the heating flow.

Schließlich beschreibt Anspruch 5 ein weiteres Beispiel einer Leitungsanordnung mit einer stirnseitig an der Brennkraftmaschine angeordneten Sammelleitung zwischen den Leitungskanälen, die einerseits mit einer Kurzschlußleitung und andererseits mit einem Wärmetauscher-Vorlauf in Verbindung steht.Finally, claim 5 describes a further example of a line arrangement with a collecting line arranged on the end face of the internal combustion engine between the line channels, which is connected on the one hand to a short-circuit line and on the other hand to a heat exchanger flow.

Die Erfindung ist anhand von in der Zeichnung dargestellten Ausführungsbeispielen beschrieben.

Fig. 1
schematisch in perspektivischer Darstellung einen flüssigkeitsgekühlten V-Motor mit maschinenmittig angeordneter Sammelleitung für den Vorlauf zu einem Kühlmittel-Wärmetauscher,
Fig. 2
eine Draufsicht auf die gemäß Linie II-II in Fig. 3 geschnittenen Zylinderköpfe, und
Fig. 3
einen Querschnitt durch die Zylinderköpfe gemäß der Linie III-III in Fig. 2, und
Fig. 4
ein weiteres Ausführungsbeispiel mit stirnseitig angeordneter Sammelleitung zwischen den Längskanälen eines V-Motors.
The invention is described with reference to exemplary embodiments shown in the drawing.
Fig. 1
schematically in perspective a liquid-cooled V-engine with a machine-centered manifold for the flow to a coolant heat exchanger,
Fig. 2
a plan view of the cylinder heads cut along line II-II in Fig. 3, and
Fig. 3
a cross section through the cylinder heads along the line III-III in Fig. 2, and
Fig. 4
a further embodiment with a collecting line arranged on the end face between the longitudinal channels of a V-engine.

Eine flüssigkeitsgekühlte Brennkraftmaschine 10 mit Zylindergehäusen 11 in V-Anordnung weist, wie aus Fig. 2 näher ersichtlich, im gegenseitigen Versatz "x" angeordnete Zylinderreihen 12 auf. Zylinderköpfe 13 der Brennkraftmaschine bzw. des V-Motors 10 weisen, wie aus den Fig. 2 und 3 hervorgeht, in einander gegenüberliegenden Längsseiten 14 angeordnete Einlaßkanäle 15 auf, während den vom V-Raum 16 abgewandten Längsseiten 14ʹ der Zylinderköpfe 13 Auslaßkanäle 17 zugeordnet sind.A liquid-cooled internal combustion engine 10 with cylinder housings 11 in a V arrangement has, as can be seen in more detail in FIG. 2, cylinder rows 12 arranged in mutual offset “x”. Cylinder heads 13 of the internal combustion engine or V-engine 10 have, as can be seen from FIGS. 2 and 3, inlet channels 15 arranged in opposite longitudinal sides 14, while the longitudinal sides 14 Läng of the cylinder heads 13 facing away from V-space 16 are assigned to 13 outlet channels 17 .

Zwischen den Einlaßkanälen 15 und den Auslaßkanälen 17 weist jeder Zylinderkopf 13 einen Kühlmittelraum 18 auf. Weiter sind die Zylinderköpfe 13 an ihren dem V-Raum 16 zugewandten Längsseiten 14 mit Längskanälen 19 ausgerüstet, die in den Zylinderköpfen 13 baulich integriert sind. Die Längskanäle 19 weisen etwa auf halber Maschinenlänge angeordnete Anschlüsse 20 auf für eine Sammelleitung 21 eines Wärmetauschervorlaufes 22 zu einem Kühlmittel-Wärmetauscher 23.Each cylinder head 13 has a coolant chamber 18 between the inlet channels 15 and the outlet channels 17. Furthermore, the cylinder heads 13 are equipped on their longitudinal sides 14 facing the V space 16 with longitudinal channels 19, which are structurally integrated in the cylinder heads 13. The longitudinal channels 19 have connections 20 arranged approximately half the length of the machine for a manifold 21 of a heat exchanger feed line 22 to a coolant heat exchanger 23.

Die Längskanäle 19 weisen in den Endbereichen der Zylinderköpfe 13 jeweils eine weitere Leitungsverbindung 24 auf, wobei die Leitungsverbindung 24 des Längskanales 19 des in Fig. 2 linken Zylinderkopfes 13 für eine Kurzschlußleitung 25 dient, während die Leitungsverbindung 24 des Längskanales 19 des rechten Zylinderkopfes 13 einem Heizungsvorlauf 26 dient. Die weitere, gestrichelt angeordnete Leitungsverbindung 24 im rechten Zylinderkopf 13 ist durch einen Blindstopfen verschlossen. Die Kurzschlußleitung 25 steht über ein Rücklauf-Thermostat 27 mit einer an der Stirnseite des V-Motors 10 angeordneten Kühlmittel-Förderpumpe 29 in Verbindung. Weiter sind die Längskanäle 19 in den anderen entgegengesetzten Endbereichen der Zylinderköpfe 13 über Querkanäle 30 mit den Kühlmittelräumen 18 verbunden. Jeder Querkanal 30 ist am Zylinderkopf 13 im Endbereich des jeweiligen Zylindergehäuses 11 mit der von einer stirnseitigen Bezugsebene 31 bzw. 32 durch den Versatz "x" maximal beabstandeten Zylinderreihe 12 angeordnet. Mit dieser Anordnung verbleibt die Baulänge jedes Zylinderkopfes 13 in der durch die beiden stirnseitigen Bezugsebenen 31 und 32 bestimmten Maschinenlänge. Die Querkanäle 30 stehen über den Auslaßkanälen 17 benachbart angeordnete Ablaufleitungen 33 mit den Kühlmittelräumen 18 der Zylinderköpfe 13 in Verbindung. Damit ist eine für V-Motore 10 mit hoher Leistung bevorzugte Querdurchströmung der Zylinderköpfe 13 erzielt.The longitudinal channels 19 each have a further line connection 24 in the end regions of the cylinder heads 13, the line connection 24 of the longitudinal channel 19 of the cylinder head 13 on the left in FIG. 2 serving for a short-circuit line 25, while the line connection 24 of the longitudinal channel 19 of the right cylinder head 13 is one Heating flow 26 is used. The further line connection 24 arranged in dashed lines in the right cylinder head 13 is closed by a blind plug. The short-circuit line 25 is connected via a return thermostat 27 to a coolant delivery pump 29 arranged on the front side of the V-engine 10. Furthermore, the longitudinal channels 19 are connected to the coolant spaces 18 in the other opposite end regions of the cylinder heads 13 via transverse channels 30. Each transverse channel 30 is arranged on the cylinder head 13 in the end region of the respective cylinder housing 11 with the cylinder row 12 which is at a maximum distance from an end reference plane 31 or 32 due to the offset “x”. With this arrangement, the overall length of each cylinder head 13 remains in the machine length determined by the two end reference planes 31 and 32. The transverse channels 30 are connected to the coolant spaces 18 of the cylinder heads 13 via the outlet channels 17 arranged adjacent drain lines 33. This is one for V-engines 10 with high performance preferred cross flow of the cylinder heads 13 achieved.

Zur Erzielung einer hohen Leistung sind jedem Zylinder der jeweiligen Zylinderreihe 12 im Zylinderkopf drei Einlaßkanäle 15 zugeordnet. Die Wandungen 34 sämtlicher Einlaßkanäle 15 eines Zylinderkopfes 13 sind miteinander verbunden und trennen im wesentlichen den Kühlmittelraum 18 vom baulich integrierten Längskanal 19. Die Wandungen 34 weisen Durchbrechungen 35 von geringem Querschnitt auf zur sicheren Ableitung von Gas- und Dampf-Blasen aus dem Kühlmittelraum 18 in den Längskanal 19.To achieve a high performance, each cylinder of the respective cylinder bank 12 in the cylinder head is assigned three inlet channels 15. The walls 34 of all the inlet channels 15 of a cylinder head 13 are connected to one another and essentially separate the coolant chamber 18 from the structurally integrated longitudinal channel 19. The walls 34 have openings 35 of small cross-section for the safe discharge of gas and vapor bubbles from the coolant chamber 18 in the longitudinal channel 19.

Das vorbeschriebene Kühlmittelfluß-System mit den Ablaufleitungen 33, den Querkanälen 30 und den Längskanälen 19 mit weiteren Leitungsverbindungen 24 und auf halber Maschinenlänge angeordneten Anschlüssen 20 für die Sammelleitung 21 des einzigen Wärmetauschervorlaufes 22 ergibt die Möglichkeit der Verwendung eines einheitlichen Zylinderkopfes 13 auf beiden Zylindergehäusen 11, wobei einer der Zylinderköpfe 13 relativ zum anderen Zylinderkopf 13 lediglich um seine Hochachse um 180° gedreht angeordnet werden kann. Mit diesem Einheits-Zylinderkopf 13 sind im wesentlichen kurze Leitungslängen für die Kurzschlußleitung 25 sowie für den Wärmetauschervorlauf 22 erzielbar.The above-described coolant flow system with the drain lines 33, the transverse channels 30 and the longitudinal channels 19 with further line connections 24 and connections 20 arranged over half the length of the machine for the manifold 21 of the single heat exchanger flow 22 results in the possibility of using a uniform cylinder head 13 on both cylinder housings 11, wherein one of the cylinder heads 13 can be arranged relative to the other cylinder head 13 only rotated by 180 ° about its vertical axis. With this unit cylinder head 13 essentially short line lengths for the short-circuit line 25 and for the heat exchanger flow 22 can be achieved.

Schließlich zeigt die Fig. 4 eine Brennkraftmaschine 100, bei der die Anschlüsse für eine Sammelleitung 210 identisch sind mit in den Endbereichen der Zylinderköpfe 130 angeordneten Leitungsverbindungen 240 der Längskanäle 190. Die gesonderten, gestrichelt angedeuteten Anschlüsse 20 der Längskanäle 190 sind durch Blindstopfen verschlossen. Die Sammelleitung 210 steht einerseits mit einer Kurzschlußleitung 250 und andererseits mit einem Wärmetauscher-Vorlauf 220 in Verbindung.Finally, FIG. 4 shows an internal combustion engine 100 in which the connections for a manifold 210 are identical to line connections 240 of the longitudinal channels 190 arranged in the end regions of the cylinder heads 130. The separate connections 20 of the longitudinal channels 190, indicated by dashed lines, are closed by blind plugs. The manifold 210 is connected on the one hand to a short-circuit line 250 and on the other hand to a heat exchanger flow 220.

Claims (5)

  1. A unitary cylinder head for liquid-cooled internal combustion engines with oppositely-disposed cylinder blocks, more particularly V-engines,
    - the cylinder heads (13, 130) of an internal combustion engine (10, 100) each having a longitudinal duct (19, 190) on facing longitudinal sides, and
    - the longitudinal ducts (19, 190) being connected to coolant chambers (18) in the cylinder heads (13, 130) so that
    - the coolant flowing out of the cylinder blocks (11, 110) into the coolant chambers (18) in the cylinder heads (13, 130) is supplied through the longitudinal ducts (19, 190) to separate coolant pipes (21, 210; 25, 250; 26) which can be optionally connected to the internal combustion engine (10, 100), characterised in that
    - the unit cylinder heads (13, 130) each have transverse ducts (30) in oppositely-disposed free end portions of the cylinder block (11) resulting from an offset (x) of the rows (12) of cylinders, and
    - the transverse ducts connect the coolant chambers (18) in the cylinder heads (13, 130) to longitudinal ducts (19, 190) disposed separately from the coolant chambers and conveying the coolant in counter-current relative to the longitudinal flow in the coolant chambers (18).
  2. A unitary cylinder head according to claim 1, characterised in that
    - the coolant chamber (18) is provided substantially between inlet ducts (15) and outlet ducts (17) arranged in accordance with the transverse-flow principle, and
    - the longitudinal duct (19, 190) is incorporated in the unit cylinder head (13, 130) so that
    - interconnected walls (34) of the inlet ducts (15) substantially separate the longitudinal duct (19, 190) from the coolant chamber (18).
  3. A unitary cylinder head according to claims 1 and 2, characterised in that
    - a discharge pipe (33) is disposed adjacent the outlet ducts (17) and
    - additionally connects the coolant chamber (18) to the transverse duct (30).
  4. A unitary cylinder head according to claims 1 to 3, characterised in that
    - each longitudinal duct (19) has a connection (20), disposed about half way along the engine, for a manifold (21) of a heat exchange pipe (22) connecting the unit cylinder heads (13), and
    - the connection (24) of one longitudinal duct (19) serves as a short-circuit pipe (25) and the connection (24) of the other longitudinal duct (19) serves as a heating pipe (26).
  5. A unitary cylinder head according to claims 1 to 3, characterised in that
    - the connections for a manifold (210) are identical with connections (240) disposed in an end region of the internal combustion engine (100), the manifold (210) being connected to additional pipes (220, 250).
EP88103084A 1987-03-17 1988-03-01 Cylinder heads for v-type internal-combustion engines Expired - Lifetime EP0282808B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3708673 1987-03-17
DE3708673 1987-03-17

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EP0282808A2 EP0282808A2 (en) 1988-09-21
EP0282808A3 EP0282808A3 (en) 1989-07-26
EP0282808B1 true EP0282808B1 (en) 1991-10-16

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DE (1) DE3865468D1 (en)
ES (1) ES2026583T3 (en)

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Publication number Priority date Publication date Assignee Title
JP2929500B2 (en) * 1990-09-04 1999-08-03 ヤマハ発動機株式会社 Cooling structure of 4-cycle engine
KR950003062B1 (en) * 1990-10-31 1995-03-30 스즈끼 가부시끼가이샤 V-engine construction
DE10338778B4 (en) * 2003-08-23 2006-05-18 Adam Opel Ag Cylinder head for an internal combustion engine
FR2947767B1 (en) * 2009-07-08 2011-10-28 Peugeot Citroen Automobiles Sa POWERTRAIN UNIT WITH A COOLING CIRCUIT AND VEHICLE EQUIPPED WITH SUCH A POWERTRAIN GROUP

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1629664A (en) * 1921-09-02 1927-05-24 Gen Motors Corp Internal-combustion engine
US2713332A (en) * 1953-03-27 1955-07-19 Int Harvester Co Internal combustion engine cooling system
US2963007A (en) * 1954-07-12 1960-12-06 Gen Motors Corp Engine with reversible heads, couplings, and gaskets
US2936745A (en) * 1958-12-31 1960-05-17 Gen Motors Corp Engine cooling system
GB1279132A (en) * 1969-04-02 1972-06-28 Chrysler United Kingdom Ltd Fo Improvements in or relating to internal combustion engines
JPS58107840A (en) * 1981-12-22 1983-06-27 Nissan Motor Co Ltd Cooling device of v-type internal-combustion engine
DE3473002D1 (en) * 1983-04-21 1988-09-01 Mazda Motor V-TYPE ENGINE

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ES2026583T3 (en) 1992-05-01
EP0282808A3 (en) 1989-07-26
EP0282808A2 (en) 1988-09-21
DE3865468D1 (en) 1991-11-21

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