EP0580651B1 - Internal-combustion engine - Google Patents
Internal-combustion engine Download PDFInfo
- Publication number
- EP0580651B1 EP0580651B1 EP92908047A EP92908047A EP0580651B1 EP 0580651 B1 EP0580651 B1 EP 0580651B1 EP 92908047 A EP92908047 A EP 92908047A EP 92908047 A EP92908047 A EP 92908047A EP 0580651 B1 EP0580651 B1 EP 0580651B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cylinder
- cylinder head
- combustion engine
- internal combustion
- engine according
- 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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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
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- 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
- F02F1/38—Cylinder heads having cooling means for liquid cooling the cylinder heads being of overhead valve type
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis
Definitions
- the invention relates to an internal combustion engine according to the preamble of the main claim.
- An internal combustion engine is known from DE-PS 348632, the cylinder head of which is of lightweight construction. However, this does not support the cylinder head plate in the middle in any way.
- GB-A-724461 discloses a cylinder head with a flat lower wall which delimits the cylinder space and with a plurality of inlet and outlet ducts which can be closed by a valve.
- the intake and exhaust ports have an arc from the central direction in the lower region of the cylinder head at an angle of 90 ° to a radial extent to the outside.
- the known cylinder head is used in engines which have a centrally arranged additional combustion chamber which communicates with the cylinder via an opening in the middle of the lower plate of the cylinder head.
- a support wall which is approximately rotationally symmetrical with respect to the central axis of the cylinder head and which extends approximately upwards from the circumference of the central bore in the lower plate of the cylinder head the shape of the horn of a trumpet diverges and opens into the upper area of the cylinder head near the surface of the cylinder, where its diameter is about three times as large as the underside, central hole.
- the support wall follows the curved course of the intake and exhaust ports up to about half the height of the cylinder head.
- the funnel-shaped support wall does not run along straight lines of force, but has an arcuate cross section due to its nestling on the course of the gas exchange channels, the curvature of which is reinforced by pressurization of the lower cylinder head plate, so that the support wall is in no way as stiff can be viewed.
- the lower cylinder head plate is additionally curved upwards, which contributes to a considerable tilting of the valves.
- the task is solved by the characteristic Features of the main claim. In this way, the compressive forces that act on the center of the cylinder head plate can be transmitted to the screws with the least possible amount of material.
- the central support is point-shaped and, due to the divergence of the cone shell-shaped support part, is also immovably fixed in all spatial directions in relation to high pressures. Since a longitudinal section through the tapered support part according to the invention always consists of straight lines, there is a particularly favorable statics, so that the cylinder head according to the invention has a maximum of stability.
- the lower cylinder head plate accordingly experiences a maximum degree of stability, in particular against deflection, so that the valve seats cannot be distorted and low wear is ensured.
- the contact zone is evenly loaded, so that there are no static Faults and therefore no leaks can occur.
- the screw supports are only connected to the half of the cylinder head facing away from the cylinder.
- the inlet and outlet channels can be designed in such a way that they are arranged only on the side of the cone-shaped support part facing the cylinder. As a result, its static stability is only broken through by the recesses for the valve stems.
- a support ring is provided which avoids contact between the two parts.
- This support ring is advantageously made of a deformable material, such as steel, in order to be able to adapt accordingly.
- This dimensionally stable sealing ring is used with approximately the same wall thickness as the cylinder top part between the cylinder top part and cylinder head.
- the shape of the upper part of the cylinder prevents the expansion of the upper end of the cylinder by the gas pressure. The result is an improved tightness of the piston above the top piston ring.
- the cooling (oil cooling) of the support ring prevents the static and thermal expansion of the upper cylinder end, so that the forces from the cylinder head are introduced into the cylinder under constant conditions.
- the shape of the inlet and outlet channels 6 and 7 is subordinate to the shape of the support cone 11 of the cylinder head 14.
- the length of the screw supports 12 in the annular bead 13 is so limited that the effect of the ring support 3 on the uniform distribution of force over the entire circumference is not affected.
- the support ring 4 has the task of ensuring gas tightness with the uniform circumferential force of the screw pressure.
- the bore slugs 17 for valve guidance protrude beyond the cone-shaped support part 11.
- Fig. 2 shows the ring plate 13, which holds all four cylinder head screws in a direct frictional connection and also guarantees the introduction of the screw forces into the rigid support cone 11.
- FIG. 3 shows a longitudinal section like FIG. 1 in the region of the support ring 4 through the cylinder 8 and the cylinder head 14 of a piston internal combustion engine, the piston 18 being in the uppermost piston position.
- a rigid metal sealing and support ring 4 protrudes over the cylinder 8 and encloses it and protrudes into the cylinder head 14.
Landscapes
- 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)
- Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
- Glass Compositions (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Die Erfindung geht aus von einer Brennkraftmaschine nach dem Oberbegriff des Hauptanspruchs.The invention relates to an internal combustion engine according to the preamble of the main claim.
Aus der DE-PS 348632 ist eine Brennkraftmaschine bekannt, deren Zylinderkopf in Leichtbauweise ausgeführt ist. Dadurch ist jedoch die Zylinderkopfplatte in der Mitte in keiner Weise abgestützt. Durch die enormen Drücke, die bei modernen Motoren, insbesondere Dieselmotoren, entstehen, kann es zu einer Durchbiegen der Zylinderkopfplatte kommen, wobei es zu starken Verschleißerscheinungen an den Ventilsitzen kommt.An internal combustion engine is known from DE-PS 348632, the cylinder head of which is of lightweight construction. However, this does not support the cylinder head plate in the middle in any way. The enormous pressures that occur in modern engines, especially diesel engines, can cause the cylinder head plate to bend, causing severe wear and tear on the valve seats.
Die GB-A-724461 offenbart einen Zylinderkopf mit einer flachen unteren Wand, die den Zylinderraum begrenzt, sowie mit mehreren, durch ein Ventil verschließbaren Ein- und Auslaßkanälen. Die Ein- und Auslaßkanäle haben einen von der zentralen Richtung im unteren Bereich des Zylinderkopfes bogenförmig in einem Winkel von 90° bis zu einer radialen Erstreckung nach außen gekrümmten Verlauf. Der vorbekannte Zylinderkopf wird bei Motoren eingesetzt, die eine zentral angeordnete Zusatz-Verbrennungskammer aufweisen, die mit dem Zylinder über eine Öffnung in der Mitte der unteren Platte des Zylinderkopfs kommuniziert. Um die zwischen der zentralen Öffnung und den Ventilsitzen verbleibenden Bereiche der unteren Platte des Zylinderkopfes gegenüber dem Zylinderdruck abzustützen, dient eine zu der zentralen Achse des Zylinderkopfes etwa rotationssymmetrische Stützwand, welche von dem Umfang der zentralen Bohrung in der unteren Platte des Zylinderkopfes nach oben etwa in der Form des Schalltrichters einer Trompete divergiert und im oberen Bereich des Zylinderkopfes nahe der Mantelfläche desselben mündet, wo ihr Durchmesser etwa dreimal so groß ist wie an der unterseitigen, zentralen Bohrung. Die Stützwand folgt dem gekrümmten Verlauf der Ein- und Auslaßkanäle bis etwa zur halben Höhe des Zylinderkopfes. Zwischen dem oberen Mündungskreis der trichterförmigen Stützwand und der äußeren Mantelfläche des Zylinderkopfes befinden sich zu dessen Zentralachse parallele Bohrungen zum Durchtritt von Schrauben, mit denen der Zylinderkopf an dem Zylinder befestigt wird. Diese vorbekannte Anordnung ist mit einer Reihe von Nachteilen behaftet. Da die Stützwand sich an die Ein- und Auslaßkanäle anschmiegt, die normalerweise nicht aneinander angrenzend angeordnet sind, können die Stützwände sich nicht in der Mitte der Zylinderkopfplatte vereinigen. Der Abstützbereich hat also die Form eines Kreises, der sich bei unterschiedlichen Ausdehnungen der unteren Platte des Zylinderkopfes infolge von örtlich variierenden Temperaturen verformen kann. Infolge der vorgenannten Verformungen werden die Ventilsitze beeinträchtigt, so daß sich die Ventile stärker abnützen und der vorbekannte Motor infolge erhöhten Verschleißes frühzeitig beschädigt wird. Hierzu trägt der weitere Umstand bei, daß die trichterförmige Stützwand nicht entlang von geraden Kraftlinien verläuft, sondern infolge ihrer Anschmiegung an den Verlauf der Gaswechselkanäle einen bogenförmigen Querschnitt aufweist, dessen Wölbung durch eine Druckbeaufschlagung der unteren Zylinderkopfplatte verstärkt wird, so daß die Stützwand keinesfalls als steif angesehen werden kann. Bei einer Druckbeaufschlagung wird demnach die untere Zylinderkopfplatte zusätzlich nach oben gewölbt, was zu einer erheblichen Verkantung der Ventile beiträgt.GB-A-724461 discloses a cylinder head with a flat lower wall which delimits the cylinder space and with a plurality of inlet and outlet ducts which can be closed by a valve. The intake and exhaust ports have an arc from the central direction in the lower region of the cylinder head at an angle of 90 ° to a radial extent to the outside. The known cylinder head is used in engines which have a centrally arranged additional combustion chamber which communicates with the cylinder via an opening in the middle of the lower plate of the cylinder head. In order to support the areas of the lower plate of the cylinder head remaining between the central opening and the valve seats against the cylinder pressure, a support wall is used which is approximately rotationally symmetrical with respect to the central axis of the cylinder head and which extends approximately upwards from the circumference of the central bore in the lower plate of the cylinder head the shape of the horn of a trumpet diverges and opens into the upper area of the cylinder head near the surface of the cylinder, where its diameter is about three times as large as the underside, central hole. The support wall follows the curved course of the intake and exhaust ports up to about half the height of the cylinder head. Between the upper mouth of the funnel-shaped support wall and the outer circumferential surface of the cylinder head, there are bores parallel to its central axis for the passage of screws with which the cylinder head is fastened to the cylinder. This known arrangement has a number of disadvantages. Since the support wall nestles against the intake and exhaust ports, which are normally not arranged adjacent to one another, the support walls cannot unite in the middle of the cylinder head plate. The support area thus has the shape of a circle, which can deform at different expansions of the lower plate of the cylinder head as a result of locally varying temperatures. As a result of the aforementioned deformations, the valve seats are impaired, so that the valves wear out more and the previously known engine is damaged prematurely as a result of increased wear. This is further contributed by the fact that the funnel-shaped support wall does not run along straight lines of force, but has an arcuate cross section due to its nestling on the course of the gas exchange channels, the curvature of which is reinforced by pressurization of the lower cylinder head plate, so that the support wall is in no way as stiff can be viewed. When pressure is applied, the lower cylinder head plate is additionally curved upwards, which contributes to a considerable tilting of the valves.
Es ist die Aufgabe der Erfindung, eine Brennkraftmaschine zu schaffen, die die Nachteile des Standes der Technik vermeidet und trotz Leichtbauweise die Zylinderkopfplatte stabil hält. Gelöst wird die Aufgabe durch die kennzeichnenden Merkmale des Hauptanspruches. Auf diese Weise können die Druckkräfte, die auf die Mitte der Zylinderkopfplatte wirken, mit geringstmöglichem Materialaufwand auf die Schrauben übertragen werden.It is the object of the invention to provide an internal combustion engine which avoids the disadvantages of the prior art and keeps the cylinder head plate stable despite the lightweight construction. The task is solved by the characteristic Features of the main claim. In this way, the compressive forces that act on the center of the cylinder head plate can be transmitted to the screws with the least possible amount of material.
Indem das Stützteil die Form eines Kegelmantels aufweist, dessen gekrümmte Fläche sich in der Mitte der Zylinderkopfplatte etwa in Form einer Kegelspitze vereinigt, ist die zentrale Abstützung punktförmig ausgebildet und infolge der Divergenz des kegelmantelförmigen Stützteils auch gegenüber hohen Drücken in jeder Raumrichtung unverrückbar festgelegt. Da ein Längsschnitt durch das erfindungsgemäße, kegelmantelförmige Stützteil immer aus Geraden besteht, ergibt sich eine besonders günstige Statik, so daß der erfindungsgemäße Zylinderkopf ein Höchstmaß an Stabilität aufweist. Die untere Zylinderkopfplatte erfährt demgemäß ein Höchstmaß an Stabilität, insbesondere gegenüber Durchbiegung, so daß die Ventilsitze nicht verzogen werden können und ein niedriger Verschleiß gewährleistet ist.By the support part being in the form of a cone shell, the curved surface of which unites in the middle of the cylinder head plate approximately in the form of a cone tip, the central support is point-shaped and, due to the divergence of the cone shell-shaped support part, is also immovably fixed in all spatial directions in relation to high pressures. Since a longitudinal section through the tapered support part according to the invention always consists of straight lines, there is a particularly favorable statics, so that the cylinder head according to the invention has a maximum of stability. The lower cylinder head plate accordingly experiences a maximum degree of stability, in particular against deflection, so that the valve seats cannot be distorted and low wear is ensured.
Durch die massive Ausgestaltung des Ringwulstes an der dem Zylinder angewandten Seite des Zylinderkopfes wird auch bei starken Drücken das Auseinanderstreben der Befestigungspunkte verhindert. Dies tritt selbst dann ein, wenn pro Zylinder nur vier Schrauben verwendet werden.Due to the massive design of the annular bead on the side of the cylinder head facing the cylinder, the fastening points are prevented from spreading apart even under strong pressures. This occurs even if only four screws are used per cylinder.
Durch die kegelstumpfförmige Ringstütze wird auch die Kontaktzone gleichmäßig belastet, so daß es zu keinen statischen Verwerfungen und damit zu keinen Undichtigkeiten kommen kann. Um die richtige Verteilung der Anpreßkräfte auf das kegelmantelförmige Stützteil und die kegelstumpfförmige Ringstütze zu gewährleisten, sind die Schraubenstützen nur mit der dem Zylinder abgewandten Hälfte des Zylinderkopfes verbunden.Due to the frustoconical ring support, the contact zone is evenly loaded, so that there are no static Faults and therefore no leaks can occur. In order to ensure the correct distribution of the contact forces on the cone-shaped support part and the frustoconical ring support, the screw supports are only connected to the half of the cylinder head facing away from the cylinder.
Da der massive Ringwulst die Befestigungspunkte für die Schrauben in einem statisch stabilen Ring verbindet, kann auf eine obere Abdeckung des Zylinderkopfes verzichtet werden. Auf diese Weise können Steuerungsteile für die Ventilschäfte bereits in den Kopf integriert werden und die Bauhöhe der Brennkraftmaschine verringert werden.Since the solid ring bead connects the fastening points for the screws in a statically stable ring, there is no need for an upper cover on the cylinder head. In this way, control parts for the valve stems can already be integrated in the head and the overall height of the internal combustion engine can be reduced.
Die Ein- und Auslaßkanäle können so gestaltet werden, daß sie nur auf der dem Zylinder zugewandten Seite des kegelmantelförmigen Stützteils angeordnet sind. Dadurch wird dieses in seiner statischen Stabilität nur noch von den Ausnehmungen für die Ventilschäfte durchbrochen.The inlet and outlet channels can be designed in such a way that they are arranged only on the side of the cone-shaped support part facing the cylinder. As a result, its static stability is only broken through by the recesses for the valve stems.
Um den Zylinder und den Zylinderkopf zu entkoppeln und so nicht zwangsläufig thermisch bedingte Verformungen von einem Teil auf das andere überzuleiten, ist ein Stützring vorgesehen, der die Berührung beider Teile vermeidet. Dieser Stützring ist in vorteilhafter Weise aus einem verformbaren Material, wie zum Beispiel Stahl, ausgeführt, um sich entsprechend anpassen zu können.In order to decouple the cylinder and the cylinder head and thus not necessarily transfer thermal deformations from one part to the other, a support ring is provided which avoids contact between the two parts. This support ring is advantageously made of a deformable material, such as steel, in order to be able to adapt accordingly.
Dieser formsteife Dichtring ist mit etwa der gleichen Wandstärke wie das Zylinderoberteil zwischen Zylinderoberteil und Zylinderkopf eingesetzt. Durch eine Formgebung, die das Zylinderoberteil umfaßt, wird die Aufweitung des oberen Endes des Zylinders durch den Gasdruck verhindert. Das Ergebnis ist eine verbesserte Dichtheit des Kolbens schon oberhalb des obersten Kolbenringes. Zuzüglich hindert die Kühlung (Ölkühlung) des Stützringes die statische und thermische Ausdehnung des oberen Zylinderendes, so daß die Kräfte aus dem Zylinderkopf unter gleichbleibenden Bedingungen in den Zylinder eingeleitet werden.This dimensionally stable sealing ring is used with approximately the same wall thickness as the cylinder top part between the cylinder top part and cylinder head. The shape of the upper part of the cylinder prevents the expansion of the upper end of the cylinder by the gas pressure. The result is an improved tightness of the piston above the top piston ring. In addition, the cooling (oil cooling) of the support ring prevents the static and thermal expansion of the upper cylinder end, so that the forces from the cylinder head are introduced into the cylinder under constant conditions.
Die Erfindung ist anhand der Zeichnungen näher erläutert. Es zeigen:
- Fig. 1 einen Längsschnitt durch einen erfindungsgemäßen Zylinderkopf und Zylinder
- Fig. 2 eine Aufsicht auf den Zylinderkopf nach Fig. 1
- Fig. 3 einen Längsschnitt wie Fig. 1 im Bereich des Stützringes.
- Fig. 1 shows a longitudinal section through a cylinder head and cylinder according to the invention
- 2 is a plan view of the cylinder head of FIG. 1st
- Fig. 3 shows a longitudinal section like Fig. 1 in the region of the support ring.
In Fig. 1 ist mit der Krafteinleitung 1 durch eine Zylinderkopfbefestigungsschraube in Schraubenöffnung 15 die nachfolgende Kraftverteilung 2 zur Mitte der Zylinderkopfplatte und über die Ringstütze 3 zum Rand und zum Stützring 4 gekennzeichnet. Damit ist sichergestellt, daß die Kopfplatte 5, die dem Gasdruck standhalten muß, der im Zylinder 8 wirksam ist, sich nicht durchbiegen kann. Jede Verformung würde die Ventilsitze 9 und 10 in Bewegung bringen, was die Standzeit des Motors durch den Verschleiß von Ventil und Sitz reduzieren würde. Auch der Misch- und Brennvorgang wird durch solche Biegeschwingungen negativ beeinflußt.In Fig. 1, the force transmission 1 by a cylinder head mounting screw in screw opening 15, the subsequent force distribution 2 to the center of the cylinder head plate and via the ring support 3 to the edge and to the
Die Form der Ein- und Auslaßkanäle 6 und 7 ist der Form des Stützkegels 11 des Zylinderkopfes 14 untergeordnet.The shape of the inlet and
Die Länge der Schraubenstützen 12 im Ringwulst 13 ist so begrenzt, daß die Wirkung der Ringstütze 3 auf die gleichmäßige Kraftverteilung auf den ganzen Umfang nicht beeinflußt wird. Der Stützring 4 hat die Aufgabe, mit der gleichmäßigen Umfangskraft des Schraubendruckes die Gasdichtheit zu gewährleisten. Die Bohrungsbutzen 17 zur Ventilführung überragen das kegelmantelförmige Stützteil 11.The length of the screw supports 12 in the
Fig. 2 zeigt die Ringplatte 13, die alle vier Zylinderkopfschrauben in direktem Kraftschluß zusammenhält und auch die Einleitung der Schraubenkräfte in den formsteifen Stützkegel 11 garantiert.Fig. 2 shows the
Die Fig. 3 zeigt einen Längsschnitt wie Fig. 1 im Bereich des Stützringes 4 durch den Zylinder 8 und den Zylinderkopf 14 einer Kolbenbrennkraftmaschine, wobei der Kolben 18 sich in oberster Kolbenstellung befindet. Ein formsteifer metallener Dicht- und Stützring 4 ragt über den Zylinder 8 und umschließt ihn und ragt in den Zylinderkopf 14 hinein. Ein Kühlmedium 19, vorzugsweise Öl, umspült das obere Teil des Zylinders im Bereich des Ringträgers des Kolbens 18; eine Kühlmanschette 20 dichtet die Kühlflüssigkeit 19 nach außen ab.FIG. 3 shows a longitudinal section like FIG. 1 in the region of the
Claims (9)
- Internal combustion engine comprising at least one cylinder (8), whose compression-side aperture is sealed with a cylinder head (14), which is bolted to the cylinder (8) and in which the contact zone between the cylinder (8) and the cylinder head (14) is circular and lies within a circle defined by the anchorage points of the bolts in the cylinder (8), characterised in that the cylinder head (14) has on its side remote from the cylinder (8) a solid annular bead (13), in which the bolt holes (15) are disposed, and a hollow-conical support member (11), by means of which a portion of the contact pressure forces (1) is transmitted by the bolts via the annular bead (13) and in a straight line (2) to the centre of the cylinder head plate (5).
- Internal combustion engine according to claim 1, characterised in that a portion of the contact pressure forces (1) is transmitted via the annular bead (13) and a frustoconical annular bracket (3) in a straight line to the contact zone.
- Internal combustion engine according to claim 1, characterised in that the straight joining lines between the bolts extend in the plane (16) of power transfer within the annular bead (13).
- Internal combustion engine according to claim 1, characterised in that on the half of the cylinder head (14) remote from the cylinder (8), support elements (12) with bolt holes (15) for receiving respective cylinder head fixing bolts are provided.
- Internal combustion engine according to claim 1, characterised in that the cylinder head (14) is open on its side remote from the cylinder (8).
- Internal combustion engine according to claim 1, characterised in that the inlet and outlet ports (6) and (7) are so arranged in the cylinder head (14) that they fit the hollow-conical support member (11), which is perforated only by the valve stem recesses.
- Internal combustion engine according to claim 1, characterised in that the contact between the cylinder (8) and the cylinder head (14) is formed by a support ring (4).
- Internal combustion engine according to claim 7, characterised in that the support ring (4) encompasses the cylinder (8).
- Internal combustion engine according to claim 7, characterised in that the support ring (4) encompasses the cylinder head (14) at the level of the valve seats.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19914111716 DE4111716A1 (en) | 1991-04-10 | 1991-04-10 | IC engine with lightweight cylinder head - head is fastened by screws through annular ring to direct contact pressure to cylinder head plate |
| DE4111716 | 1991-04-10 | ||
| DE4124999 | 1991-07-27 | ||
| DE4124999 | 1991-07-27 | ||
| PCT/DE1992/000296 WO1992018762A1 (en) | 1991-04-10 | 1992-04-10 | Internal-combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0580651A1 EP0580651A1 (en) | 1994-02-02 |
| EP0580651B1 true EP0580651B1 (en) | 1995-10-18 |
Family
ID=25902717
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP92908047A Expired - Lifetime EP0580651B1 (en) | 1991-04-10 | 1992-04-10 | Internal-combustion engine |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US5431137A (en) |
| EP (1) | EP0580651B1 (en) |
| AT (1) | ATE129315T1 (en) |
| AU (1) | AU1545392A (en) |
| DE (1) | DE59204076D1 (en) |
| WO (1) | WO1992018762A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19734007A1 (en) * | 1997-08-06 | 1999-02-11 | Deutz Ag | Cylinder head for use with crankcases with different cylinder bore diameters |
| WO2011017262A1 (en) * | 2009-08-01 | 2011-02-10 | Electro-Motive Diesel, Inc. | Engine exhaust valve timing and lift system for a two-stroke locomotive diesel engine having an egr system |
| US8683974B2 (en) | 2011-08-29 | 2014-04-01 | Electro-Motive Diesel, Inc. | Piston |
| DE102011116372A1 (en) * | 2011-10-14 | 2013-04-18 | Vladimir Borissovskiy | Combustion chamber of a diesel engine |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE932463C (en) * | 1951-09-13 | 1955-09-01 | Viktor Dr-Ing Rembold | Pistons and cylinder covers for internal combustion engines |
| BE518964A (en) * | 1952-04-05 | |||
| DE1294096B (en) * | 1966-12-29 | 1969-04-30 | Daimler Benz Ag | Fluid-cooled cylinder head of an internal combustion engine |
| JPS57200648A (en) * | 1981-06-05 | 1982-12-08 | Nissan Motor Co Ltd | Cylinder head for overhead cam shaft engine |
| JPS58124045A (en) * | 1982-01-20 | 1983-07-23 | Suzuki Motor Co Ltd | Cylinder head for two-cycle engine |
| IT1238283B (en) * | 1990-03-23 | 1993-07-12 | Vm Motori Spa | LOCKING DEVICE FOR HEADS OF AVIO ENGINES. |
| EP0458341A1 (en) * | 1990-05-24 | 1991-11-27 | Mazda Motor Corporation | Cylinder head structure of DOHC engine |
| JPH0482343U (en) * | 1990-11-29 | 1992-07-17 |
-
1992
- 1992-04-10 US US08/133,117 patent/US5431137A/en not_active Expired - Fee Related
- 1992-04-10 DE DE59204076T patent/DE59204076D1/en not_active Expired - Fee Related
- 1992-04-10 AU AU15453/92A patent/AU1545392A/en not_active Abandoned
- 1992-04-10 AT AT92908047T patent/ATE129315T1/en not_active IP Right Cessation
- 1992-04-10 EP EP92908047A patent/EP0580651B1/en not_active Expired - Lifetime
- 1992-04-10 WO PCT/DE1992/000296 patent/WO1992018762A1/en active IP Right Grant
Also Published As
| Publication number | Publication date |
|---|---|
| DE59204076D1 (en) | 1995-11-23 |
| EP0580651A1 (en) | 1994-02-02 |
| WO1992018762A1 (en) | 1992-10-29 |
| ATE129315T1 (en) | 1995-11-15 |
| US5431137A (en) | 1995-07-11 |
| AU1545392A (en) | 1992-11-17 |
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