EP1329628B1 - Cylinder head for a piston combustion engine with a cooling conduit system - Google Patents

Cylinder head for a piston combustion engine with a cooling conduit system Download PDF

Info

Publication number
EP1329628B1
EP1329628B1 EP02406107A EP02406107A EP1329628B1 EP 1329628 B1 EP1329628 B1 EP 1329628B1 EP 02406107 A EP02406107 A EP 02406107A EP 02406107 A EP02406107 A EP 02406107A EP 1329628 B1 EP1329628 B1 EP 1329628B1
Authority
EP
European Patent Office
Prior art keywords
cooling passage
cylinder head
roof
valve
cooling
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
Application number
EP02406107A
Other languages
German (de)
French (fr)
Other versions
EP1329628A3 (en
EP1329628A2 (en
Inventor
Walter Keller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP02406107A priority Critical patent/EP1329628B1/en
Publication of EP1329628A2 publication Critical patent/EP1329628A2/en
Publication of EP1329628A3 publication Critical patent/EP1329628A3/en
Application granted granted Critical
Publication of EP1329628B1 publication Critical patent/EP1329628B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • F01P2003/024—Cooling cylinder heads
    • 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
    • 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
    • F01P3/16—Arrangements for cooling other engine or machine parts for cooling fuel injectors or sparking-plugs
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • 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
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines

Definitions

  • the invention relates to a cylinder cover with a cooling duct system for a reciprocating internal combustion engine according to the preamble of independent claim 1, and a reciprocating internal combustion engine with such a cylinder cover.
  • Known two-stroke diesel engines with longitudinal rinsing are known in particular as models as large diesel engines.
  • Such engines can do without intake valves in the cylinder cover, since the air enters the cylinder through so-called scavenging slots, which are arranged in the lower region of the cylinder.
  • an exhaust valve is arranged in the cylinder axis, through which the combustion gases can escape.
  • the injectors for fuel injection are arranged in a side surface of the cylinder cover, which extends obliquely with respect to the longitudinal axis of the cylinder, in suitable fitting openings. As a result, the fuel injection is not centrally, but from the side.
  • the known cylinder cover with central exhaust valve has a plurality of straight bottom cooling channels extending in the side surface of the cylinder cover, which defines a substantially conical surface, starting from a first (outer) annulus to the outlet opening, wherein the distance between two adjacent floor Cooling channels decreases towards the outlet opening.
  • the bottom cooling channel has an inlet and an outlet for a coolant, the inlet of the bottom cooling channel being farther from the outlet opening than the outlet.
  • Each outlet of a bottom cooling channel opens into a valve cooling channel, so that coolant can be conveyed successively through the bottom cooling channel and the valve cooling channel.
  • the valve cooling channels thereby extend substantially straight on a cylinder surface or on a slightly inclined conical surface along the outlet opening and open into a common second (upper) annular space, from which the coolant is back to the radiator of the internal combustion engine intimidbe blackbar.
  • the installation openings for the injection nozzles are arranged concentrically on a circular line around the outlet opening between two bottom cooling channels. In this case, the radius of the circular line is selected so that there is sufficient clearance between the corresponding floor cooling channels for the installation openings.
  • the well-known cylinder cover with central exhaust valve is characterized in particular by the fact that due to its highly symmetrical design, the thermal loads during operation with the cooling duct system briefly described above are particularly easy to control, since the simple geometry of the cylinder cover of course their Precipitation also finds in the characteristics of the temperature profile, which occurs in the operation of the large diesel engine in the cylinder cover. This means that, for example, unbalanced mechanical stresses of the cylinder cover can already be greatly minimized due to complex structured temperature gradients due to the geometry alone.
  • a serious disadvantage arises from the fact that the concept of the known cylinder cover with central exhaust valve calls for the use of several injectors, whereby this arrangement must be relatively expensive to be equipped with auxiliary units and therefore is quite expensive overall.
  • the EP 0 959 240 proposed a cylinder cover, wherein the mounting hole for the injection nozzle is located centrally in the top surface of the cylinder cover, so that only one injector is necessary for the fuel injection.
  • the outlet valve is arranged here in the side surface of the cylinder.
  • the advantages of such a cylinder cover are obvious and are in the EP 0 959 240 discussed in detail.
  • the above-described known concept of cooling the cylinder cover can not be readily transferred to a cylinder cover with a centrally arranged injection nozzle, which is already prohibitive on account of the changed geometry.
  • By arranged in the side surface outlet valve creates a significant asymmetry in the thermal load of the cylinder cover.
  • a cylinder cover with a cooling duct system for a reciprocating internal combustion engine which has at least one cylinder in which a piston is arranged back and forth along an axis of the cylinder cover, wherein the cylinder cover comprises a ceiling surface and a side surface in the assembled state Limit the combustion chamber of the cylinder.
  • the top surface of the cylinder cover there is provided an installation opening for receiving an injector through which fuel is introduced into the combustion chamber and an outlet opening arranged in the side surface relative to the axis of the cylinder cover for receiving an exhaust valve for exhausting combustion gases from the combustion chamber.
  • a plurality of floor cooling channels extending toward the outlet opening, at least two of the floor cooling channels each having an inlet and an outlet for a coolant, and a valve cooling channel extending along the outlet opening.
  • each bottom cooling channel is arranged so that the inlet of each bottom cooling channel is farther from the outlet opening than the outlet, and the outlet of at least one bottom cooling channel is connected to the valve cooling channel, so that coolant flows through the bottom one after the other. Cooling channel and the valve cooling channel is conveyed.
  • at least one nozzle cooling channel extends along the mounting opening, wherein the output of at least one bottom cooling channel is connected to the nozzle cooling channel, so that Coolant is successively conveyed through the bottom cooling channel and the nozzle cooling channel.
  • the inventive cylinder cover comprises a ceiling surface and a side surface, which limit the combustion chamber of the cylinder in the mounted state.
  • the ceiling surface of the cylinder cover forms the piston face opposite boundary surface of the combustion chamber.
  • the ceiling surface has an installation opening for an injection nozzle, which is arranged substantially centrally in the ceiling surface.
  • At the ceiling surface adjoins the side surface, which is arranged obliquely with respect to the central axis of the installation opening for the injection nozzle, so that the side surface opens at an obtuse angle in the ceiling surface.
  • the side surface has an outlet opening for receiving an outlet valve.
  • a first annular space is arranged in the cylinder cover, which is adapted to supply coolant to the cooling passage system of the cylinder cover.
  • the inventive cylinder cover is characterized by a substantially three-part ausgestaltetes cooling duct system, which, in contrast to the known cooling duct system, in addition to a plurality of bottom cooling channels and a corresponding number of valve cooling channels, additionally has a certain number of nozzle cooling channels extending along the centrally located injector.
  • the bottom cooling channels which are connected on the input side to the first annular space, substantially suitable for the cooling of the side surface, while the valve cooling channels extending along the outlet, substantially for the cooling of the cylinder cover in the region of the exhaust valve and the exhaust valve itself are provided.
  • the nozzle cooling channels extend along the installation opening and are thus suitable, in particular, for cooling the injection nozzle and the region of the cylinder cover adjacent to the installation opening.
  • the nozzle cooling channels open on the output side in a common manifold and the valve cooling channels in a common second annulus, wherein the second annulus is connected by means of a connecting line to the manifold.
  • the coolant can thus initially flow through the bottom cooling channels for cooling the side surface, starting from the first annular space, and then fed in succession through the valve cooling passages, the second annulus and the connecting line of the manifold in a first subcircuit and in parallel in a second subcircuit Subcircuit are fed through the nozzle cooling channels of the manifold, which manifold then returns the coolant back to a radiator of the reciprocating internal combustion engine.
  • Fig. 1 shows a schematic representation of a cylinder 3 of a large diesel engine G with a cylinder cover according to the invention with cooling channel system 2, which cylinder cover is hereinafter referred to in its entirety by the reference numeral 1.
  • the inventive cylinder cover 1 is particularly suitable for large diesel engines G, which are designed as two-stroke diesel engine with longitudinal rinse.
  • the essential components of large diesel engines G which generally have a plurality of cylinders 3, are known per se.
  • the cylinder 3 of such a large diesel engine G has a cylinder cover 1, which comprises a ceiling surface 5 and a side surface 6, which limit the combustion chamber 7 of the cylinder 3 in the assembled state, as shown in Fig. 1.
  • the ceiling surface 5 of the cylinder cover 1 forms the boundary surface of the combustion chamber 7 opposite the piston end face 41, which is perpendicular to an axis A -A of the cylinder cover 1.
  • the side surface 6 adjoins the ceiling surface 5, whose upper part, which opens into the ceiling surface 5, projects obliquely to the axis A - A of the cylinder cover 1, so that the side surface 6 opens into the ceiling surface 5 at an obtuse angle.
  • a piston 4 along the axis A - A arranged back and forth.
  • the piston 4 is connected by means of a piston rod in a conventional manner with a crankshaft (not shown).
  • the cylinder cover 1 has an in the ceiling surface 5, substantially centrally disposed mounting hole 8 for receiving an injection nozzle 9.
  • the injection nozzle 9 is connected via a fuel line 91 with an injection device, not shown, which introduces the fuel through the injector 9 into the combustion chamber 7 of the cylinder 3, as indicated by the dash-dotted lobes in Fig. 1.
  • an outlet opening 10 for receiving an outlet valve 11 is arranged in the side surface 6 of the cylinder cover 1.
  • the cylinder cover 1 is equipped for cooling with a substantially three-part cooling channel system 2 comprising a plurality of bottom cooling channels 12, of which at least two each have an inlet 13 and an outlet 14 for a coolant.
  • each bottom cooling channel 12 is arranged in the cylinder cover 1 such that the inlet 13 of each bottom cooling channel 12 is farther from the outlet opening 10 than its corresponding outlet 14.
  • the cylinder cover 1 comprises at least one valve cooling channel 15, and at least one nozzle cooling channel 16 with outlet opening 20, which is connected to a manifold 21.
  • FIG. 2 shows schematically a section through the inventive cylinder cover 1 with injection nozzle 9 and outlet opening 10 along a plane E, which is defined by the axes A - A and B - B.
  • a bottom cooling channel 12 which opens with its output 14 in a nozzle cooling channel 16.
  • the outlet opening 20 of the nozzle cooling channel 16 opens into the manifold 21 shown in cross-section, which is connected to a connecting line 22, whose function will be described later in detail.
  • FIGS. 3 and 4 schematically each an embodiment of a cooling passage system 2 of an inventive cylinder cover 1 with exhaust valve 11 and injector 9 is sketched in not Masstabsrater representation.
  • the injection nozzle 9 is shown in the non-installed state.
  • the generally different in their length bottom cooling channels 12 extend all, substantially rectilinearly, toward the outlet opening 10 of the cylinder cover 1.
  • the bottom cooling channels 12 in the cylinder cover 1 so arranged, that extend their longitudinal axes L - L in a conical surface, starting from a first annular space 17 to the axis A - A to the center of the cylinder cover 1, wherein the angle ⁇ between the longitudinal axes L - L of any two adjacent floor cooling channels 12 substantially always the same.
  • the angle ⁇ between different pairs of longitudinal axes L - L is different.
  • the first annular space 17 is disposed within the cylinder cover 1 at its periphery and is connected via a supply line 171 with a cooling device of the cylinder 3, not shown, through which supply line 171 the first annulus 17 coolant from the (not shown) cooling device of the cylinder 3 can be fed ,
  • the first annular space 17 may well have a plurality of supply lines 171 or the supply line 171 may extend as an annular opening partially or completely along the first annular space 17.
  • Each of these bottom cooling channels 12 is preferably connected to exactly one valve cooling channel 15 in each case. However, it is quite conceivable that two or more such bottom cooling channels 12 are connected simultaneously to one and the same valve cooling channel 15.
  • Each valve cooling passage 15 preferably extends rectilinearly at a certain inclination angle with respect to the axis V-V of the exhaust port 10 along the axis V-V. Here, the inclination angle with respect to the axis V-V may be the same for all the valve cooling passages 15.
  • the angle of inclination with respect to the axis V-V may be zero degrees, so that all the valve cooling channels 15 lie on a common (imaginary) cylinder surface; at another value of the angle of inclination, all the valve cooling channels 15 lie on a (imaginary) conical surface.
  • two or more of the valve cooling channels with respect to the axis V - V have different angles of inclination, e.g. to compensate for an asymmetry of the temperature distribution in the cylinder cover with respect to the axis V - V during operation.
  • one or more valve cooling channels 15 do not extend in a straight line along the outlet opening 10, but extend in a spiral shape or in another form with respect to the axis V-V.
  • valve cooling channel 15 opens, starting from the output 14 of a bottom cooling channel 12 into a second annular space 18, which receives the successively the bottom cooling channel 12 and the valve cooling channel 15 by flowing coolant is suitable, and from which the coolant is again supplied via a connecting line 22 to a manifold 21, which manifold 21 is adapted to return the coolant to a not shown cooler of the large diesel engine G.
  • two or more such bottom cooling channels 12 are connected at their output 14 simultaneously with one and the same nozzle cooling channel 15.
  • Each nozzle cooling passage 16 preferably extends in a straight line at a certain angle with respect to the axis A - A of the cylinder cover 1 along the axis A - A.
  • the angle with respect to the axis A - A for all nozzles -Kühlkanäle 16 be the same or different.
  • one or more nozzle cooling channels 16 do not extend in a straight line along the installation opening 8, but extend in a spiral shape or in another form with respect to the axis A-A.
  • the nozzle cooling channel 16 extending along the installation opening 8 emanates from the outlet 14 of a bottom cooling channel 12 into the collecting line 21, which is suitable for receiving the coolant flowing successively through the bottom cooling channel 12 and the nozzle cooling channel 16, and via which Manifold 21, the coolant is again discharged to the cooler of the large diesel engine G, not shown.
  • both a part of the bottom cooling channels, as well as the valve cooling channels and / or the nozzle cooling channels are designed as blind holes, that is, that the respective channels only an inlet opening for a coolant, however have no outlet opening. It is also conceivable that the diameter of the various cooling channels is designed differently, so that by different areas within the cylinder cover per unit time flow different amounts of coolant, which asymmetric thermal loads on the cylinder cover can be better compensated.
  • the cylinder cover according to the invention thus comprises a cooling channel system which, due to its substantially three-part construction, is particularly well adapted to the requirements for cooling a cylinder cover with central fuel injection and laterally arranged outlet valve. Due to the additional use of nozzle cooling channels and the special geometry and arrangement of the various cooling channels, the highly asymmetric thermal load of the cylinder cover is optimally taken into account, so that the locally varying amounts of heat generated during operation by the cooling channel system can be dissipated in such a way that temperature gradients are effectively reduced and thus mechanical Tensioning in the cylinder cover can be effectively avoided.

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)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft einen Zylinderdeckel mit einem Kühlkanalsystem für eine Hubkolbenbrennkraftmaschine gemäss dem Oberbegriff des unabhängigen Anspruchs 1, sowie eine Hubkolbenbrennkraftmaschine mit einem solchen Zylinderdeckel.The invention relates to a cylinder cover with a cooling duct system for a reciprocating internal combustion engine according to the preamble of independent claim 1, and a reciprocating internal combustion engine with such a cylinder cover.

Bekannte Zweitakt-Dieselbrennkraftmaschinen mit Längsspülung sind insbesondere in Ausführungen als Grossdieselmotoren bekannt. Solche Motoren kommen ohne Einlassventile im Zylinderdeckel aus, da die Luft durch sogenannte Spülschlitze, die im unteren Bereich des Zylinders angeordnet sind, in den Zylinder eintritt. In einer Deckenfläche im zentralen Bereich des Zylinderdeckels ist ein Auslassventil in der Zylinderachse angeordnet, durch das die Verbrennungsgase austreten können. Die Einspritzdüsen für die Brennstoffeinspritzung sind dagegen in einer Seitenfläche des Zylinderdeckels, die schräg bezüglich der Längsachse des Zylinders verläuft, in dafür geeigneten Einbauöffnungen angeordnet. Dadurch erfolgt die Brennstoffeinspritzung nicht zentral, sondern von der Seite. Um dennoch eine möglichst gleichmässige Verteilung des eingespritzten Brennstoffs im Brennraum zu erreichen, sind pro Zylinder mehrere Einspritzdüsen, typischerweise drei pro Zylinder, vorgesehen. Der Vorteil eines Zylinderdeckels mit zentral angeordnetem Auslassventil liegt unter anderem darin, dass die Ausführung und Anordnung des Kühlsystems im Zylinderdeckel besonders einfach ist. Durch die hohe Symmetrie der Anordnung von Auslassventil und Einspritzdüsen ergibt sich eine ebenfalls bezüglich der zentralen Auslassöffnung des Zylinderdeckels hohe Symmetrie der thermischen Belastungen des Zylinderdeckels im Betrieb. Entsprechend einfach ist daher auch die Geometrie bekannter Kühlkanalsysteme für solche Zylinderdeckel.Known two-stroke diesel engines with longitudinal rinsing are known in particular as models as large diesel engines. Such engines can do without intake valves in the cylinder cover, since the air enters the cylinder through so-called scavenging slots, which are arranged in the lower region of the cylinder. In a ceiling surface in the central region of the cylinder cover, an exhaust valve is arranged in the cylinder axis, through which the combustion gases can escape. On the other hand, the injectors for fuel injection are arranged in a side surface of the cylinder cover, which extends obliquely with respect to the longitudinal axis of the cylinder, in suitable fitting openings. As a result, the fuel injection is not centrally, but from the side. In order nevertheless to achieve the most uniform possible distribution of the injected fuel in the combustion chamber, several injection nozzles, typically three per cylinder, are provided per cylinder. The advantage of a Cylinder head with centrally located exhaust valve is, among other things, that the design and arrangement of the cooling system in the cylinder cover is particularly simple. Due to the high symmetry of the arrangement of exhaust valve and injectors results in a likewise with respect to the central outlet opening of the cylinder cover high symmetry of the thermal loads of the cylinder cover during operation. Correspondingly simple is therefore the geometry of known cooling duct systems for such cylinder cover.

Der bekannte Zylinderdeckel mit zentralem Auslassventil weist eine Vielzahl von geraden Boden-Kühlkanälen auf, die sich in der Seitenfläche des Zylinderdeckels, die im wesentlichen eine Kegelmantelfläche definiert, von einem ersten (äusseren) Ringraum ausgehend zur Auslassöffnung hin erstrecken, wobei der Abstand zweier benachbarter Boden-Kühlkanäle zur Auslassöffnung hin abnimmt. Der Boden-Kühlkanal weist dabei einen Eingang und einen Ausgang für ein Kühlmittel auf, wobei der Eingang des Boden-Kühlkanals weiter von der Auslassöffnung entfernt ist als der Ausgang. Jeder Ausgang eines Boden-Kühlkanals mündet in einen Ventil-Kühlkanal, so dass Kühlmittel nacheinander durch den Boden-Kühlkanal und den Ventil-Kühlkanal beförderbar ist. Die Ventil-Kühlkanäle erstrecken sich dabei im wesentlichen auf einer Zylinderoberfläche oder auf einer leicht geneigten Kegeloberfläche geradlinig entlang der Auslassöffnung und münden in einen gemeinsamen zweiten (oberen) Ringraum, von welchem aus das Kühlmittel wieder zum Kühler der Brennkraftmaschine zurückbeförderbar ist. Die Einbauöffnungen für die Einspritzdüsen sind konzentrisch auf einer Kreislinie um die Auslassöffnung zwischen je zwei Boden-Kühlkanälen angeordnet. Dabei wird der Radius der Kreislinie so gewählt, dass für die Einbauöffnungen genügend Zwischenraum zwischen den entsprechenden Boden-Kühlkanälen zur Verfügung steht.The known cylinder cover with central exhaust valve has a plurality of straight bottom cooling channels extending in the side surface of the cylinder cover, which defines a substantially conical surface, starting from a first (outer) annulus to the outlet opening, wherein the distance between two adjacent floor Cooling channels decreases towards the outlet opening. The bottom cooling channel has an inlet and an outlet for a coolant, the inlet of the bottom cooling channel being farther from the outlet opening than the outlet. Each outlet of a bottom cooling channel opens into a valve cooling channel, so that coolant can be conveyed successively through the bottom cooling channel and the valve cooling channel. The valve cooling channels thereby extend substantially straight on a cylinder surface or on a slightly inclined conical surface along the outlet opening and open into a common second (upper) annular space, from which the coolant is back to the radiator of the internal combustion engine zurückbeförderbar. The installation openings for the injection nozzles are arranged concentrically on a circular line around the outlet opening between two bottom cooling channels. In this case, the radius of the circular line is selected so that there is sufficient clearance between the corresponding floor cooling channels for the installation openings.

Der bekannte Zylinderdeckel mit zentralem Auslassventil zeichnet sich insbesondere dadurch aus, dass aufgrund seines hoch symmetrischen Aufbaus auch die thermischen Belastungen im Betrieb mit dem zuvor kurz beschriebenen Kühlkanalsystem besonders einfach zu kontrollieren sind, da die einfache Geometrie des Zylinderdeckels selbstverständlich ihren Niederschlag auch in der Charakteristik des Temperaturprofils findet, das sich im Betrieb des Grossdieselmotors im Zylinderdeckel einstellt. Das heisst, dass beispielsweise unsymmetrische mechanische Verspannungen des Zylinderdeckels aufgrund von komplex strukturierten Temperaturgradienten allein aufgrund der Geometrie bereits stark minimierbar sind. Ein gravierender Nachteil ergibt sich jedoch aus der Tatsache, dass das Konzept des bekannten Zylinderdeckels mit zentralem Auslassventil den Einsatz mehrerer Einspritzdüsen fordert, wodurch diese Anordnung relativ aufwendig mit Zusatzaggregaten ausgestattet werden muss und daher insgesamt recht kostenintensiv ist.The well-known cylinder cover with central exhaust valve is characterized in particular by the fact that due to its highly symmetrical design, the thermal loads during operation with the cooling duct system briefly described above are particularly easy to control, since the simple geometry of the cylinder cover of course their Precipitation also finds in the characteristics of the temperature profile, which occurs in the operation of the large diesel engine in the cylinder cover. This means that, for example, unbalanced mechanical stresses of the cylinder cover can already be greatly minimized due to complex structured temperature gradients due to the geometry alone. However, a serious disadvantage arises from the fact that the concept of the known cylinder cover with central exhaust valve calls for the use of several injectors, whereby this arrangement must be relatively expensive to be equipped with auxiliary units and therefore is quite expensive overall.

Zur Beseitigung dieser Nachteile wurde mit der EP 0 959 240 ein Zylinderdeckel vorgeschlagen, bei welchem sich die Einbauöffnung für die Einspritzdüse zentral in der Deckenfläche des Zylinderdeckels befindet, so dass für die Brennstoffeinspritzung nur noch eine Einspritzdüse notwendig ist. Das Auslassventil ist hier in der Seitenfläche des Zylinders angeordnet. Die Vorteile eines solchen Zylinderdeckels liegen auf der Hand und sind in der EP 0 959 240 ausführlich diskutiert. Allerdings lässt sich das oben beschriebene bekannte Konzept der Kühlung des Zylinderdeckels nicht ohne weiteres auf einen Zylinderdeckel mit zentral angeordneter Einspritzdüse übertragen, was sich alleine schon aufgrund der geänderten Geometrie verbietet. Durch das in der Seitenfläche angeordnete Auslassventil entsteht eine erhebliche Asymmetrie in der thermischen Belastung des Zylinderdeckels. So treten in der Nähe des Auslassventils im Betrieb deutlich höhere Temperaturen auf, als beispielsweise in der Nähe der Einspritzdüse. Damit stellen sich an die Art der Wärmeabführung vollkommen andere Anforderungen, als bei einem Zylinderdeckel mit zentralem Auslassventil. Das Kühlkanalsystems für einen Zylinderdeckel mit zentraler Einspritzdüse muss daher völlig neu konzipiert werden.To eliminate these disadvantages was with the EP 0 959 240 proposed a cylinder cover, wherein the mounting hole for the injection nozzle is located centrally in the top surface of the cylinder cover, so that only one injector is necessary for the fuel injection. The outlet valve is arranged here in the side surface of the cylinder. The advantages of such a cylinder cover are obvious and are in the EP 0 959 240 discussed in detail. However, the above-described known concept of cooling the cylinder cover can not be readily transferred to a cylinder cover with a centrally arranged injection nozzle, which is already prohibitive on account of the changed geometry. By arranged in the side surface outlet valve creates a significant asymmetry in the thermal load of the cylinder cover. In operation, significantly higher temperatures occur in the vicinity of the outlet valve than, for example, in the vicinity of the injection nozzle. Thus, the type of heat dissipation completely different requirements than with a cylinder cover with central exhaust valve. The cooling duct system for a cylinder cover with central injection nozzle must therefore be completely redesigned.

Es ist daher die Aufgabe der Erfindung, einen Zylinderdeckel mit einem Kühlkanalsystem für eine Hubkolbenbrennkraftmaschine mit Längsspülung, insbesondere für einen als Zweitakt-Dieselbrennkraftmaschine ausgelegten Grossdieselmotor vorzuschlagen, wobei das Kühlkanalsystem die besonderen Erfordemisse an die Kühlung eines Zylinderdeckels mit zentral angeordneter Einspritzdüse und einem asymmetrisch in einer Seitenfläche des Zylinderdeckels angeordneten Auslassventil berücksichtigt.It is therefore an object of the invention to provide a cylinder cover with a cooling duct system for a reciprocating internal combustion engine with a longitudinal purge, especially for a designed as a two-stroke diesel engine large diesel engine, the cooling duct system the special Erfordemisse to the cooling of a cylinder cover with centrally arranged Injector and an asymmetrically arranged in a side surface of the cylinder cover exhaust valve considered.

Die diese Aufgabe lösenden Gegenstände der Erfindung sind durch die Merkmale des unabhängigen Anspruchs 1 gekennzeichnet.The problem-solving objects of the invention are characterized by the features of independent claim 1.

Die abhängigen Ansprüche beziehen sich auf besonders vorteilhafte Ausführungen der Erfindung.The dependent claims relate to particularly advantageous embodiments of the invention.

Erfindungsgemäss wird somit ein Zylinderdeckel mit einem Kühlkanalsystem für eine Hubkolbenbrennkraftmaschine vorgeschlagen, die mindestens einen Zylinder aufweist, in welchem ein Kolben entlang einer Achse des Zylinderdeckels hin- und herbewegbar angeordnet ist, wobei der Zylinderdeckel eine Deckenfläche und eine Seitenfläche umfasst, die im montierten Zustand den Brennraum des Zylinders begrenzen. In der Deckenfläche des Zylinderdeckels ist eine Einbauöffnung zur Aufnahme einer Einspritzdüse, durch die Brennstoff in den Brennraum einbringbar ist, und eine in Bezug zur Achse des Zylinderdeckels in der Seitenfläche angeordnete Auslassöffnung zur Aufnahme eines Auslassventils zum Abführen von Verbrennungsgasen aus dem Brennraum vorgesehen. Desweiteren eine Mehrzahl von Boden-Kühlkanälen, die sich in Richtung zur Auslassöffnung erstrecken, wobei mindestens zwei der Boden-Kühlkanäle jeweils einen Eingang und einen Ausgang für ein Kühlmittel aufweisen, sowie einen Ventil-Kühlkanal, der sich längs der Auslassöffnung erstreckt. Dabei ist jeder Boden-Kühlkanal so angeordnet, dass der Eingang jedes Boden-Kühlkanals weiter von der Auslassöffnung entfernt ist als der Ausgang, und der Ausgang mindestens eines Boden-Kühlkanals mit dem Ventil-Kühlkanal verbunden ist, so dass Kühlmittel nacheinander durch den Boden-Kühlkanal und den Ventil-Kühlkanal beförderbar ist. Zusätzlich erstreckt sich mindestens ein Düsen-Kühlkanal entlang der Einbauöffnung, wobei der Ausgang mindestens eines Boden-Kühlkanals mit dem Düsen-Kühlkanal verbunden ist, so dass Kühlmittel nacheinander durch den Boden-Kühlkanal und den Düsen-Kühlkanal beförderbar ist.According to the invention, a cylinder cover with a cooling duct system for a reciprocating internal combustion engine is proposed, which has at least one cylinder in which a piston is arranged back and forth along an axis of the cylinder cover, wherein the cylinder cover comprises a ceiling surface and a side surface in the assembled state Limit the combustion chamber of the cylinder. In the top surface of the cylinder cover there is provided an installation opening for receiving an injector through which fuel is introduced into the combustion chamber and an outlet opening arranged in the side surface relative to the axis of the cylinder cover for receiving an exhaust valve for exhausting combustion gases from the combustion chamber. Further, a plurality of floor cooling channels extending toward the outlet opening, at least two of the floor cooling channels each having an inlet and an outlet for a coolant, and a valve cooling channel extending along the outlet opening. In this case, each bottom cooling channel is arranged so that the inlet of each bottom cooling channel is farther from the outlet opening than the outlet, and the outlet of at least one bottom cooling channel is connected to the valve cooling channel, so that coolant flows through the bottom one after the other. Cooling channel and the valve cooling channel is conveyed. In addition, at least one nozzle cooling channel extends along the mounting opening, wherein the output of at least one bottom cooling channel is connected to the nozzle cooling channel, so that Coolant is successively conveyed through the bottom cooling channel and the nozzle cooling channel.

Der erfindungsgemässe Zylinderdeckel umfasst eine Deckenfläche und eine Seitenfläche, die im montierten Zustand, den Brennraum des Zylinders begrenzen. Dabei bildet die Deckenfläche des Zylinderdeckels die der Kolbenstirnfläche gegenüberliegende Begrenzungsfläche des Brennraums. Die Deckenfläche weist eine Einbauöffnung für eine Einspritzdüse auf, die im wesentlichen zentral in der Deckenfläche angeordnet ist. An die Deckenfläche schliesst sich die Seitenfläche an, welche schrägt in Bezug zur Mittelachse der Einbauöffnung für die Einspritzdüse angeordnet ist, so dass die Seitenfläche stumpfwinklig in die Deckenfläche einmündet. Die Seitenfläche weist eine Auslassöffnung zur Aufnahme eines Auslassventils auf. In der Peripherie der Seitenfläche ist im Zylinderdeckel ein erster Ringraum angeordnet, der dazu geeignet ist, dem Kühlkanalsystem des Zylinderdeckels Kühlmittel zuzuführen.The inventive cylinder cover comprises a ceiling surface and a side surface, which limit the combustion chamber of the cylinder in the mounted state. In this case, the ceiling surface of the cylinder cover forms the piston face opposite boundary surface of the combustion chamber. The ceiling surface has an installation opening for an injection nozzle, which is arranged substantially centrally in the ceiling surface. At the ceiling surface adjoins the side surface, which is arranged obliquely with respect to the central axis of the installation opening for the injection nozzle, so that the side surface opens at an obtuse angle in the ceiling surface. The side surface has an outlet opening for receiving an outlet valve. In the periphery of the side surface, a first annular space is arranged in the cylinder cover, which is adapted to supply coolant to the cooling passage system of the cylinder cover.

Der erfindungsgemässe Zylinderdeckel zeichnet sich durch ein im wesentlichen dreiteilig ausgestaltetes Kühlkanalsystem aus, das, im Gegensatz zu dem bekannten Kühlkanalsystem, neben einer Vielzahl von Boden-Kühlkanälen und einer entsprechenden Anzahl von Ventil-Kühlkanälen, zusätzlich noch eine bestimmte Zahl von Düsen-Kühlkanälen aufweist, die sich entlang der zentral angeordneten Einspritzdüse erstrecken. Dabei sind die Boden-Kühlkanäle, die eingangsseitig mit dem ersten Ringraum verbunden sind, im wesentlichen für die Kühlung der Seitenfläche geeignet, während die Ventil-Kühlkanäle, die sich entlang der Auslassöffnung erstrecken, im wesentlichen für die Kühlung des Zylinderdeckels im Bereich des Auslassventils und des Auslassventils selbst vorgesehen sind. Die Düsen-Kühlkanäle erstrecken sich entlang der Einbauöffnung und sind damit insbesondere zur Kühlung der Einspritzdüse und des an die Einbauöffnung angrenzenden Bereichs des Zylinderdeckels geeignet. Dabei ist ein Teil der zuvor erwähnten Boden-Kühlkanäle ausgangsseitig mit den Ventil-Kühlkanälen verbunden, während die übrigen verbleibenden Boden-Kühlkanäle ausgangsseitig mit den Düsen-Kühlkanälen verbunden sind. Die Düsen-Kühlkanäle münden ausgangsseitig in eine gemeinsame Sammelleitung und die Ventil-Kühlkanäle in einen gemeinsamen zweiten Ringraum, wobei der zweite Ringraum mittels einer Verbindungsleitung mit der Sammelleitung verbunden ist.The inventive cylinder cover is characterized by a substantially three-part ausgestaltetes cooling duct system, which, in contrast to the known cooling duct system, in addition to a plurality of bottom cooling channels and a corresponding number of valve cooling channels, additionally has a certain number of nozzle cooling channels extending along the centrally located injector. In this case, the bottom cooling channels, which are connected on the input side to the first annular space, substantially suitable for the cooling of the side surface, while the valve cooling channels extending along the outlet, substantially for the cooling of the cylinder cover in the region of the exhaust valve and the exhaust valve itself are provided. The nozzle cooling channels extend along the installation opening and are thus suitable, in particular, for cooling the injection nozzle and the region of the cylinder cover adjacent to the installation opening. It is part of the previously mentioned bottom cooling channels connected on the output side with the valve cooling channels, while the remaining remaining bottom cooling channels are connected on the output side to the nozzle cooling channels. The nozzle cooling channels open on the output side in a common manifold and the valve cooling channels in a common second annulus, wherein the second annulus is connected by means of a connecting line to the manifold.

Im Betrieb kann somit das Kühlmittel ausgehend vom ersten Ringraum zunächst die Boden-Kühlkanäle zur Kühlung der Seitenfläche durchströmen, und anschliessend in einem ersten Teilkreislauf nacheinander durch die Ventil-Kühlkanäle, den zweiten Ringraum und die Verbindungsleitung der Sammelleitung zugeführt werden und parallel dazu in einem zweiten Teilkreislauf durch die Düsen-Kühlkanäle der Sammelleitung zugeführt werden, welche Sammelleitung dann das Kühlmittel wieder zu einem Kühler der Hubkolbenbrennkraftmaschine zurückführt.During operation, the coolant can thus initially flow through the bottom cooling channels for cooling the side surface, starting from the first annular space, and then fed in succession through the valve cooling passages, the second annulus and the connecting line of the manifold in a first subcircuit and in parallel in a second subcircuit Subcircuit are fed through the nozzle cooling channels of the manifold, which manifold then returns the coolant back to a radiator of the reciprocating internal combustion engine.

Die Erfindung wird im Folgenden an Hand der Zeichnung näher erläutert. Es zeigen in schematischer Darstellung:

Fig. 1
einen Zylinder eines Grossdieselmotors mit Zylinderdeckel und weiteren wesentlichen Teilen;
Fig. 2
ein Ausführungsbeispiel eines erfindungsgemässen Zylinderdeckels mit Kühlkanalsystem im Schnitt;
Fig. 3
eine nicht massstabsgerechte Darstellung eines ersten Ausführungsbeispiels eines Kühlkanalsystems mit Auslassventil und Einspritzdüse;
Fig. 4
ein zweites Ausführungsbeispiel gemäss Fig. 3.
The invention will be explained in more detail below with reference to the drawing. In a schematic representation:
Fig. 1
a cylinder of a large diesel engine with cylinder cover and other essential parts;
Fig. 2
an embodiment of an inventive cylinder cover with cooling channel system in section;
Fig. 3
a not to scale representation of a first embodiment of a cooling duct system with exhaust valve and injector;
Fig. 4
A second embodiment according to FIG. 3.

Fig. 1 zeigt in einer schematischen Darstellung einen Zylinder 3 eines Grossdieselmotors G mit einem erfindungsgemässen Zylinderdeckel mit Kühlkanalsystem 2, welcher Zylinderdeckel im folgenden gesamthaft mit dem Bezugszeichen 1 bezeichnet ist. Der erfindungsgemässe Zylinderdeckel 1 ist insbesondere für Grossdieselmotoren G geeignet, die als Zweitakt-Dieselbrennkraftmaschinen mit Längsspülung ausgelegt sind. Die wesentlichen Komponenten von Grossdieselmotoren G, die in der Regel mehrere Zylinder 3 aufweisen, sind an sich bekannt.Fig. 1 shows a schematic representation of a cylinder 3 of a large diesel engine G with a cylinder cover according to the invention with cooling channel system 2, which cylinder cover is hereinafter referred to in its entirety by the reference numeral 1. The inventive cylinder cover 1 is particularly suitable for large diesel engines G, which are designed as two-stroke diesel engine with longitudinal rinse. The essential components of large diesel engines G, which generally have a plurality of cylinders 3, are known per se.

Der Zylinder 3 eines solchen Grossdieselmotors G weist einen Zylinderdeckel 1 auf, der eine Deckenfläche 5 und eine Seitenfläche 6 umfasst, die im montierten Zustand, wie in Fig. 1 gezeigt, den Brennraum 7 des Zylinders 3 begrenzen. Dabei bildet die Deckenfläche 5 des Zylinderdeckels 1 im montierten Zustand die der Kolbenstirnfläche 41 gegenüberliegende Begrenzungsfläche des Brennraums 7, die senkrecht zu einer Achse A -A des Zylinderdeckels 1 liegt. An die Deckenfläche 5 schliesst sich die Seitenfläche 6 an, deren darstellungsgemäss oberer Teil, welcher in die Deckenfläche 5 einmündet, schrägt zur Achse A - A des Zylinderdeckels 1 verläuft, so dass die Seitenfläche 6 stumpfwinklig in die Deckenfläche 5 einmündet. Im Zylinder 3 ist ein Kolben 4 entlang der Achse A - A hin- und herbewegbar angeordnet. Der Kolben 4 ist mittels einer Kolbenstange in an sich bekannter Weise mit einer Kurbelwelle (nicht dargestellt) verbunden.The cylinder 3 of such a large diesel engine G has a cylinder cover 1, which comprises a ceiling surface 5 and a side surface 6, which limit the combustion chamber 7 of the cylinder 3 in the assembled state, as shown in Fig. 1. In the assembled state, the ceiling surface 5 of the cylinder cover 1 forms the boundary surface of the combustion chamber 7 opposite the piston end face 41, which is perpendicular to an axis A -A of the cylinder cover 1. The side surface 6 adjoins the ceiling surface 5, whose upper part, which opens into the ceiling surface 5, projects obliquely to the axis A - A of the cylinder cover 1, so that the side surface 6 opens into the ceiling surface 5 at an obtuse angle. In the cylinder 3, a piston 4 along the axis A - A arranged back and forth. The piston 4 is connected by means of a piston rod in a conventional manner with a crankshaft (not shown).

Der Zylinderdeckel 1 weist eine in der Deckenfläche 5, im wesentlichen zentral, angeordnete Einbauöffnung 8 zur Aufnahme einer Einspritzdüse 9 auf. Die Einspritzdüse 9 ist über eine Brennstoffleitung 91 mit einer nicht dargestellten Einspritzvorrichtung verbunden, die den Brennstoff durch die Einspritzdüse 9 in den Brennraum 7 des Zylinders 3 einbringt, wie dies die strichpunktierten Keulen in Fig. 1 andeuten. In der Seitenfläche 6 des Zylinderdeckels 1 ist eine Auslassöffnung 10 zur Aufnahme eines Auslassventils 11 angeordnet.The cylinder cover 1 has an in the ceiling surface 5, substantially centrally disposed mounting hole 8 for receiving an injection nozzle 9. The injection nozzle 9 is connected via a fuel line 91 with an injection device, not shown, which introduces the fuel through the injector 9 into the combustion chamber 7 of the cylinder 3, as indicated by the dash-dotted lobes in Fig. 1. In the side surface 6 of the cylinder cover 1, an outlet opening 10 for receiving an outlet valve 11 is arranged.

Der Zylinderdeckel 1 ist zur Kühlung mit einem im wesentlichen dreiteiligen Kühlkanalsystem 2 ausgestattet, das eine Mehrzahl von Boden-Kühlkanälen 12 umfasst, von denen mindestens zwei jeweils einen Eingang 13 und einen Ausgang 14 für ein Kühlmittel aufweisen. Dabei ist jeder Boden-Kühlkanal 12 im Zylinderdeckel 1 so angeordnet, dass der Eingang 13 eines jeden Boden-Kühlkanals 12 weiter von der Auslassöffnung 10 entfernt ist, als sein entsprechender Ausgang 14. Darüber hinaus umfasst der Zylinderdeckel 1 mindestens einen Ventil-Kühlkanal 15, sowie mindestens einen Düsen-Kühlkanal 16 mit Austrittsöffnung 20, welcher mit einer Sammelleitung 21 verbunden ist.The cylinder cover 1 is equipped for cooling with a substantially three-part cooling channel system 2 comprising a plurality of bottom cooling channels 12, of which at least two each have an inlet 13 and an outlet 14 for a coolant. In this case, each bottom cooling channel 12 is arranged in the cylinder cover 1 such that the inlet 13 of each bottom cooling channel 12 is farther from the outlet opening 10 than its corresponding outlet 14. In addition, the cylinder cover 1 comprises at least one valve cooling channel 15, and at least one nozzle cooling channel 16 with outlet opening 20, which is connected to a manifold 21.

In Fig.2 ist schematisch ein Schnitt durch den erfindungsgemässen Zylinderdeckel 1 mit Einspritzdüse 9 und Auslassöffnung 10 entlang einer Ebene E dargestellt, die durch die Achsen A - A und B - B definiert ist. Zu erkennen ist ein Boden-Kühlkanal 12, welcher mit seinem Ausgang 14 in einen Düsen-Kühlkanal 16 mündet. Die Austrittsöffnung 20 des Düsen-Kühlkanals 16 mündet in die im Querschnitt dargestellte Sammelleitung 21, welche mit einer Verbindungsleitung 22 verbunden ist, deren Funktion später noch ausführlich beschrieben wird.2 shows schematically a section through the inventive cylinder cover 1 with injection nozzle 9 and outlet opening 10 along a plane E, which is defined by the axes A - A and B - B. Evident is a bottom cooling channel 12, which opens with its output 14 in a nozzle cooling channel 16. The outlet opening 20 of the nozzle cooling channel 16 opens into the manifold 21 shown in cross-section, which is connected to a connecting line 22, whose function will be described later in detail.

In den Fig. 3 und 4 ist schematisch je ein Ausführungsbeispiel eines Kühlkanalsystems 2 eines erfindungsgemässen Zylinderdeckels 1 mit Auslassventil 11 und Einspritzdüse 9 in nicht masstabsgerechter Darstellung skizziert. Der Übersicht halber ist die Einspritzdüse 9 im nicht eingebauten Zustand dargestellt. Wie aus den Fig. 3 und 4 ersichtlich ist, erstrecken sich die in ihrer Länge im allgemeinen unterschiedlichen Boden-Kühlkanäle 12 sämtlich, im wesentlichen geradlinig, in Richtung zur Auslassöffnung 10 des Zylinderdeckels 1. Bevorzugt sind die Boden-Kühlkanäle 12 im Zylinderdeckel 1 so angeordnet, dass sich deren Längsachsen L - L in einer Kegelmantelfläche, ausgehend von einem ersten Ringraum 17 zur Achse A - A zum Zentrum des Zylinderdeckels 1 erstrecken, wobei der Winkel α zwischen den Längsachsen L - L zweier beliebiger benachbarter Boden-Kühlkanäle 12 im wesentlichen immer gleich ist. Denkbar ist natürlich auch, dass der Winkel α zwischen verschiedenen Paaren von Längsachsen L - L unterschiedlich ist.In Figs. 3 and 4 schematically each an embodiment of a cooling passage system 2 of an inventive cylinder cover 1 with exhaust valve 11 and injector 9 is sketched in not Masstabsgerechter representation. For the sake of clarity, the injection nozzle 9 is shown in the non-installed state. As can be seen from FIGS. 3 and 4, the generally different in their length bottom cooling channels 12 extend all, substantially rectilinearly, toward the outlet opening 10 of the cylinder cover 1. Preferably, the bottom cooling channels 12 in the cylinder cover 1 so arranged, that extend their longitudinal axes L - L in a conical surface, starting from a first annular space 17 to the axis A - A to the center of the cylinder cover 1, wherein the angle α between the longitudinal axes L - L of any two adjacent floor cooling channels 12 substantially always the same. Of course, it is also conceivable that the angle α between different pairs of longitudinal axes L - L is different.

Der erste Ringraum 17 ist innerhalb des Zylinderdeckels 1 an dessen Peripherie angeordnet und ist über eine Zuleitungseinrichtung 171 mit einer nicht gezeigten Kühleinrichtung des Zylinders 3 verbunden, durch welche Zuleitungseinrichtung 171 dem ersten Ringraum 17 Kühlmittel aus der (nicht gezeigten) Kühleinrichtung des Zylinders 3 zuführbar ist. Dabei kann der erste Ringraum 17 durchaus mehrere Zuleitungseinrichtungen 171 aufweisen oder die Zuleitungseinrichtung 171 kann sich als ringförmige Öffnung teilweise oder ganz entlang des ersten Ringraumes 17 erstrecken.The first annular space 17 is disposed within the cylinder cover 1 at its periphery and is connected via a supply line 171 with a cooling device of the cylinder 3, not shown, through which supply line 171 the first annulus 17 coolant from the (not shown) cooling device of the cylinder 3 can be fed , In this case, the first annular space 17 may well have a plurality of supply lines 171 or the supply line 171 may extend as an annular opening partially or completely along the first annular space 17.

Diejenigen Boden-Kühlkanäle 12, deren Ausgänge 14 näher an der Auslassöffnung 10 als an der Einbauöffnung 8 liegen, sind über den Ausgang 14 mit einem Ventil-Kühlkanal 15 verbunden. Bevorzugt steht jeder dieser Boden-Kühlkanäle 12 jeweils mit genau einem Ventil-Kühlkanal 15 in Verbindung. Allerdings ist es durchaus denkbar, dass zwei oder mehrere solcher Boden-Kühlkanäle 12 gleichzeitig mit ein und demselben Ventil-Kühlkanal 15 verbunden ist. Jeder Ventil-Kühlkanal 15 erstreckt sich bevorzugt geradlinig unter einem bestimmten Neigungswinkel bezüglich der Achse V - V der Auslassöffnung 10 entlang der Achse V - V. Dabei kann der Neigungswinkel bezüglich der Achse V - V für alle Ventil-Kühlkanäle 15 gleich sein. Zum Beispiel kann der Neigungswinkel bezüglich der Achse V - V null Grad betragen, so dass alle Ventil-Kühlkanäle 15 auf einer gemeinsamen (gedachten) Zylinderfläche liegen; bei einem anderen Wert des Neigungswinkels liegen alle Ventil-Kühlkanäle 15 auf einer (gedachten) Kegelfläche. Selbstverständlich ist es auch denkbar, dass zwei oder mehrere der Ventil-Kühlkanäle bezüglich der Achse V - V verschiedene Neigungswinkel aufweisen, um z.B. eine bezüglich der Achse V - V im Betrieb auftretende Asymmetrie der Temperaturverteilung im Zylinderdeckel zu kompensieren. In besonderen Fällen ist es auch denkbar, dass sich ein oder mehrere Ventil-Kühlkanäle 15 nicht geradlinig entlang der Auslassöffnung 10 erstrecken, sondern sich bezüglich der Achse V - V spiralförmig oder in einer anderen Form erstrecken.Those ground cooling channels 12, whose outlets 14 are closer to the outlet opening 10 than to the installation opening 8, are connected via the outlet 14 to a valve cooling channel 15. Each of these bottom cooling channels 12 is preferably connected to exactly one valve cooling channel 15 in each case. However, it is quite conceivable that two or more such bottom cooling channels 12 are connected simultaneously to one and the same valve cooling channel 15. Each valve cooling passage 15 preferably extends rectilinearly at a certain inclination angle with respect to the axis V-V of the exhaust port 10 along the axis V-V. Here, the inclination angle with respect to the axis V-V may be the same for all the valve cooling passages 15. For example, the angle of inclination with respect to the axis V-V may be zero degrees, so that all the valve cooling channels 15 lie on a common (imaginary) cylinder surface; at another value of the angle of inclination, all the valve cooling channels 15 lie on a (imaginary) conical surface. Of course, it is also conceivable that two or more of the valve cooling channels with respect to the axis V - V have different angles of inclination, e.g. to compensate for an asymmetry of the temperature distribution in the cylinder cover with respect to the axis V - V during operation. In special cases, it is also conceivable that one or more valve cooling channels 15 do not extend in a straight line along the outlet opening 10, but extend in a spiral shape or in another form with respect to the axis V-V.

Der sich entlang der Auslassöffnung 10 erstreckende Ventil-Kühlkanal 15 mündet ausgehend vom Ausgang 14 eines Boden-Kühlkanals 12 in einen zweiten Ringraum 18, der zur Aufnahme des nacheinander den Boden-Kühlkanal 12 und den Ventil-Kühlkanal 15 durchströmende Kühlmittel geeignet ist, und aus welchem das Kühlmittel wieder über eine Verbindungsleitung 22 einer Sammelleitung 21 zuführbar ist, welche Sammelleitung 21 dazu geeignet ist, das Kühlmittel einem nicht gezeigten Kühler des Grossdieselmotors G zurückzuführen.The extending along the outlet opening 10 valve cooling channel 15 opens, starting from the output 14 of a bottom cooling channel 12 into a second annular space 18, which receives the successively the bottom cooling channel 12 and the valve cooling channel 15 by flowing coolant is suitable, and from which the coolant is again supplied via a connecting line 22 to a manifold 21, which manifold 21 is adapted to return the coolant to a not shown cooler of the large diesel engine G.

Diejenigen Boden-Kühlkanäle 12, deren Ausgänge 14 näher an der Einbauöffnung 8, als an der Auslassöffnung 10 liegen, sind über den Ausgang 14 mit einem Düsen-Kühlkanal 16 verbunden. Bevorzugt steht jeder dieser Boden-Kühlkanäle 12, wie in Fig. 3 dargestellt, jeweils mit genau einem Düsen-Kühlkanal 16 in Verbindung. Allerdings ist es durchaus denkbar, dass zwei oder mehrere solcher Boden-Kühlkanäle 12 an ihrem Ausgang 14 gleichzeitig mit ein und demselben Düsen-Kühlkanal 15 verbunden sind. Ein solches Ausführungsbeispiel zeigt Fig. 4. Jeder Düsen-Kühlkanal 16 erstreckt sich bevorzugt geradlinig unter einem bestimmten Winkel bezüglich der Achse A - A des Zylinderdeckels 1 entlang der Achse A - A. Dabei kann der Winkel bezüglich der Achse A - A für alle Düsen-Kühlkanäle 16 gleich oder verschieden sein. In besonderen Fällen ist es auch denkbar, dass sich ein oder mehrere Düsen-Kühlkanäle 16 nicht geradlinig entlang der Einbauöffnung 8 erstrecken, sondern sich bezüglich der Achse A - A spiralförmig oder in einer anderen Form erstrecken.Those ground cooling channels 12 whose outlets 14 are located closer to the installation opening 8 than to the outlet opening 10 are connected via the outlet 14 to a nozzle cooling channel 16. Preferably, each of these bottom cooling channels 12, as shown in Fig. 3, each with exactly one nozzle cooling channel 16 in connection. However, it is quite conceivable that two or more such bottom cooling channels 12 are connected at their output 14 simultaneously with one and the same nozzle cooling channel 15. Such an embodiment is shown in FIG. 4. Each nozzle cooling passage 16 preferably extends in a straight line at a certain angle with respect to the axis A - A of the cylinder cover 1 along the axis A - A. In this case, the angle with respect to the axis A - A for all nozzles -Kühlkanäle 16 be the same or different. In special cases, it is also conceivable that one or more nozzle cooling channels 16 do not extend in a straight line along the installation opening 8, but extend in a spiral shape or in another form with respect to the axis A-A.

Der sich entlang der Einbauöffnung 8 erstreckende Düsen-Kühlkanal 16 mündet ausgehend vom Ausgang 14 eines Boden-Kühlkanals 12 in die Sammelleitung 21, die zur Aufnahme des nacheinander den Boden-Kühlkanal 12 und den Düsen-Kühlkanal 16 durchströmende Kühlmittel geeignet ist, und über welche Sammelleitung 21 das Kühlmittel wieder zu dem nicht gezeigten Kühler des Grossdieselmotors G abführbar ist.The nozzle cooling channel 16 extending along the installation opening 8 emanates from the outlet 14 of a bottom cooling channel 12 into the collecting line 21, which is suitable for receiving the coolant flowing successively through the bottom cooling channel 12 and the nozzle cooling channel 16, and via which Manifold 21, the coolant is again discharged to the cooler of the large diesel engine G, not shown.

Unter Umständen kann es von Vorteil sein, dass sowohl ein Teil der Boden-Kühlkanäle, als auch der Ventil-Kühlkanäle und / oder der Düsen-Kühlkanäle als Blindbohrungen ausgeführt sind, das heisst, dass die entsprechenden Kanäle nur eine Eingangsöffnung für ein Kühlmittel, jedoch keine Ausgangsöffnung aufweisen. Ebenso ist es denkbar, dass der Durchmesser der verschiedenen Kühlkanäle unterschiedlich ausgelegt ist, so dass durch verschiedene Bereiche innerhalb des Zylinderdeckels pro Zeiteinheit unterschiedliche Mengen an Kühlmittel fliessen, wodurch asymmetrische thermische Belastungen des Zylinderdeckels besser ausgeglichen werden können.Under certain circumstances, it may be advantageous that both a part of the bottom cooling channels, as well as the valve cooling channels and / or the nozzle cooling channels are designed as blind holes, that is, that the respective channels only an inlet opening for a coolant, however have no outlet opening. It is also conceivable that the diameter of the various cooling channels is designed differently, so that by different areas within the cylinder cover per unit time flow different amounts of coolant, which asymmetric thermal loads on the cylinder cover can be better compensated.

Der erfindungsgemässe Zylinderdeckel umfasst somit ein Kühlkanalsystem, welches aufgrund seines im wesentlichen dreiteiligen Aufbaus den Anforderungen an die Kühlung eines Zylinderdeckels mit zentraler Kraftstoffeinspritzung und seitlich angeordnetem Auslassventil besonders gut angepasst ist. Durch den zusätzlichen Einsatz von Düsen-Kühlkanälen und die spezielle Geometrie und Anordnung der verschiedenen Kühlkanäle wird die stark asymmetrische thermische Belastung des Zylinderdeckels optimal berücksichtigt, wodurch die im Betrieb entstehenden lokal unterschiedlichen Wärmemengen durch das Kühlkanalsystem so abführbar sind, dass Temperaturgradienten wirksam abgebaut und damit mechanische Verspannungen im Zylinderdeckel wirksam vermieden werden können.The cylinder cover according to the invention thus comprises a cooling channel system which, due to its substantially three-part construction, is particularly well adapted to the requirements for cooling a cylinder cover with central fuel injection and laterally arranged outlet valve. Due to the additional use of nozzle cooling channels and the special geometry and arrangement of the various cooling channels, the highly asymmetric thermal load of the cylinder cover is optimally taken into account, so that the locally varying amounts of heat generated during operation by the cooling channel system can be dissipated in such a way that temperature gradients are effectively reduced and thus mechanical Tensioning in the cylinder cover can be effectively avoided.

Claims (10)

  1. A cylinder head having a cooling passage system (2) for a reciprocating internal combustion engine which has at least one cylinder (3) in which a piston (4) is arranged movable to and fro along an axis (A - A) of the cylinder head, the cylinder head including:
    - a roof area (5) and a side area (6) which bound the combustion chamber (7) of the cylinder (3) in the mounted state;
    - a mounting opening (8) arranged in the roof area (5) for receiving an injection nozzle (9) through which fuel can be introduced into the combustion chamber (7);
    - an outlet opening (10) arranged with respect to the axis (A - A) in the side area (6) for receiving an outlet valve (11) for discharging combustion gases from the combustion chamber (7);
    - a plurality of roof cooling passages (12) which extend in the direction of the outlet opening (10), with at least two of the roof cooling passages (12) each having an inlet (13) and an outlet (14) for a coolant;
    - a valve cooling passage (15) which extends along the outlet opening (10);
    with each roof cooling passage (12) being arranged such that the inlet (13) of the roof cooling passage (12) is further removed from the outlet opening (10) than the outlet (14) and that the outlet (14) of at least one roof cooling passage (12) is connected to the valve cooling passage (15) so that coolant can be successively transported through the roof cooling passage (12) and the valve cooling passage (15), characterised in that at least one nozzle cooling passage (16) extends along the mounting opening (8), with the outlet (14) of at least one roof cooling passage (12) being connected to the nozzle cooling passage (16) such that coolant can be successively transported through the roof cooling passage (12) and the nozzle cooling passage (16).
  2. A cylinder head in accordance with claim 1, wherein the inlet (13) of the roof cooling passage (12) is in communication with a first annular space (17) from which coolant can be supplied to the inlet (13) of the roof cooling passage (12).
  3. A cylinder head in accordance with claim 1 or claim 2, wherein the valve cooling passage (15) opens into a second annular space (18) which is suitable for receiving coolant.
  4. A cylinder head in accordance with any one of claims 1 to 3, wherein at least two roof cooling passages (12) and/or two valve cooling passages (15) differ in their diameters.
  5. A cylinder head in accordance with any one of claims 1 to 4, wherein at least two valve cooling passages (15) and/or two nozzle cooling passages (16) differ in their diameters.
  6. A cylinder head in accordance with any one of claims 1 to 5, wherein a longitudinal axis (L - L) of the roof cooling passage (12) is disposed on a conical surface and extends, starting from the first annular space, to the axis (A - A) of the cylinder head.
  7. A cylinder head in accordance with any one of claims 1 to 6, wherein the outlets (14) of at least two roof cooling passages (12) are connected via a connection passage (19).
  8. A cylinder head in accordance with any one of claims 1 to 7, wherein an outlet opening (20) of the nozzle cooling passage (16) is connected to a manifold (21).
  9. A cylinder head in accordance with any one of claims 1 to 8, wherein the manifold (21) is in communication with the second annular space (18) via a connection line (22) for the passing on of coolant.
  10. A reciprocating internal combustion engine, in particular a large diesel engine, having a cylinder head in accordance with any one of claims 1 to 9.
EP02406107A 2002-01-16 2002-12-17 Cylinder head for a piston combustion engine with a cooling conduit system Expired - Lifetime EP1329628B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02406107A EP1329628B1 (en) 2002-01-16 2002-12-17 Cylinder head for a piston combustion engine with a cooling conduit system

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP02405023 2002-01-16
EP02405023 2002-01-16
EP02406107A EP1329628B1 (en) 2002-01-16 2002-12-17 Cylinder head for a piston combustion engine with a cooling conduit system

Publications (3)

Publication Number Publication Date
EP1329628A2 EP1329628A2 (en) 2003-07-23
EP1329628A3 EP1329628A3 (en) 2003-11-19
EP1329628B1 true EP1329628B1 (en) 2007-06-13

Family

ID=27635916

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02406107A Expired - Lifetime EP1329628B1 (en) 2002-01-16 2002-12-17 Cylinder head for a piston combustion engine with a cooling conduit system

Country Status (7)

Country Link
EP (1) EP1329628B1 (en)
JP (1) JP4340070B2 (en)
KR (1) KR100921412B1 (en)
CN (1) CN100467847C (en)
DE (1) DE50210310D1 (en)
DK (1) DK1329628T3 (en)
PL (1) PL358264A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8151743B2 (en) 2007-06-30 2012-04-10 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Cooling channels in the cylinder head of an internal combustion engine

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2410140B1 (en) 2010-07-20 2013-05-08 Wärtsilä Schweiz AG lubrication device for a piston
EP3000998B1 (en) * 2014-09-24 2017-07-19 Caterpillar Motoren GmbH & Co. KG Valve seat insert for an internal combustion engine
KR20160068044A (en) * 2014-12-04 2016-06-15 현대자동차주식회사 Engine for vihicles
DK179175B1 (en) * 2016-03-16 2018-01-08 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland A cylinder cover for a large two-stroke turbocharged compression-ignited internal combustion engine
EP3219970A1 (en) * 2016-03-17 2017-09-20 Winterthur Gas & Diesel AG Cylinder for a longitudinally wound two-stroke large disel engine and large diesel engine
JP7164286B2 (en) 2016-04-27 2022-11-01 東芝ライフスタイル株式会社 refrigerator

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH242922A (en) * 1944-05-08 1946-06-15 Sulzer Ag Internal combustion engine.
CH545915A (en) * 1971-12-09 1974-02-15
JP3073275B2 (en) * 1991-07-24 2000-08-07 ヤンマーディーゼル株式会社 Cylinder head of water-cooled internal combustion engine
EP0959240B1 (en) 1998-05-22 2003-09-24 Wärtsilä Schweiz AG Cylinder head and arrangement for a two-stroke diesel engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8151743B2 (en) 2007-06-30 2012-04-10 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Cooling channels in the cylinder head of an internal combustion engine

Also Published As

Publication number Publication date
EP1329628A3 (en) 2003-11-19
CN100467847C (en) 2009-03-11
CN1432727A (en) 2003-07-30
EP1329628A2 (en) 2003-07-23
PL358264A1 (en) 2003-07-28
JP2003214251A (en) 2003-07-30
DK1329628T3 (en) 2007-10-08
JP4340070B2 (en) 2009-10-07
DE50210310D1 (en) 2007-07-26
KR100921412B1 (en) 2009-10-14
KR20030077948A (en) 2003-10-04

Similar Documents

Publication Publication Date Title
EP1870591B1 (en) Intake device for an internal combustion engine
AT506473B1 (en) CYLINDER HEAD OF AN INTERNAL COMBUSTION ENGINE
DE102007062347B4 (en) Cooling arrangement for a cylinder head of an internal combustion engine
DE102008035957B4 (en) Cylinder head for an internal combustion engine
EP3379063A1 (en) Liquid-cooled combustion engine
EP1516113A1 (en) Cooled cylinder head for a reciprocating engine
DE10331918B4 (en) Cylinder head for a liquid-cooled multi-cylinder internal combustion engine
WO2020011926A1 (en) Cylinder head and crankcase for an internal combustion engine
EP0771941A1 (en) Internal combustion engine cylinder head
EP1329628B1 (en) Cylinder head for a piston combustion engine with a cooling conduit system
DE19546545B4 (en) intake manifold
DE102004047990B4 (en) Air intake arrangement for an internal combustion engine
AT524566B1 (en) Liquid-cooled internal combustion engine
EP0819837A1 (en) Cooling circuit of an internal combustion engine
DE10047080B4 (en) Cooling system for a liquid-cooled internal combustion engine
DE3806031A1 (en) MULTI-CYLINDER ENGINE BLOCK FOR A TWO-STROKE COMBUSTION ENGINE
DE102014204031B4 (en) Exhaust gas recirculation device for vehicle engines
EP0921286B1 (en) Direct injection type internal combustion engine
AT520539B1 (en) INTERNAL COMBUSTION ENGINE WITH AN OUTLET CHANNEL ARRANGEMENT
WO2005088111A1 (en) Water-cooled cylinder head for an internal combustion engine
DE102016216360B4 (en) Cylinder head for an internal combustion engine
DE102020111055B3 (en) Cylinder head with a cooling channel structure
EP0637680A1 (en) Liquid cooled multicylinder internal combustion engine
DE4416251C1 (en) Exhaust port for IC engine
DE102015222859A1 (en) Cylinder head of an internal combustion engine with integrated exhaust manifold and cooling jacket

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

17P Request for examination filed

Effective date: 20040420

AKX Designation fees paid

Designated state(s): DE DK FI FR IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE DK FI FR IT

REF Corresponds to:

Ref document number: 50210310

Country of ref document: DE

Date of ref document: 20070726

Kind code of ref document: P

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20080314

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20081222

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20081212

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20081219

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20091214

Year of fee payment: 8

Ref country code: FI

Payment date: 20091215

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091217

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101217