EP1965068A1 - Air gap insulation on a cylinder socket - Google Patents
Air gap insulation on a cylinder socket Download PDFInfo
- Publication number
- EP1965068A1 EP1965068A1 EP08151490A EP08151490A EP1965068A1 EP 1965068 A1 EP1965068 A1 EP 1965068A1 EP 08151490 A EP08151490 A EP 08151490A EP 08151490 A EP08151490 A EP 08151490A EP 1965068 A1 EP1965068 A1 EP 1965068A1
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- EP
- European Patent Office
- Prior art keywords
- cylinder liner
- insert ring
- height
- air gap
- recess
- 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.)
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Classifications
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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
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
- F02F1/16—Cylinder liners of wet type
Definitions
- the invention relates to a cylinder liner for an internal combustion engine, in particular for a gas engine, with a crankcase in which a crankshaft is rotatably mounted on which at least one connecting rod carrying a piston is articulated, wherein in the cylinder liner, a piston between a lower and a top dead center in an axial direction K is movable, wherein the cylinder liner has a cylinder liner collar through which the cylinder liner is inserted or fixed in a housing of the internal combustion engine, and wherein a cylinder head side recess is provided, in which an insert ring with a height h R is inserted.
- the insert ring is usually designed and arranged so that a top, recessed into the piston piston ring groove projects at the TDC position of the piston to the insert ring.
- Such a cylinder liner for an internal combustion engine is known from DE 1 900 922 B known.
- the teaching of this document is concerned with making available a piston-cylinder liner arrangement in which, despite the presence of an enlarged annular space between the piston and cylinder liner, an oil carbon coating which could contact the cylinder inner wall is avoided in precisely this clearance.
- This is achieved in that the inner wall of the cylinder liner has a diameter-reduced portion at its combustion chamber end.
- This section is going through one in the Cylinder liner recessed insert ring produced, wherein the insert ring is preferably made of the same material as the cylinder liner and is firmly inserted into the recess.
- a cylinder liner is described with a Zylinderbüchsenbund having a cylinder head side recess into which an insert ring is inserted.
- the insert ring is made of a thermally more stable material than the cylinder liner and serves to prevent deposits on the piston.
- a recess is provided within the outer wall, so that a direct heat flow is prevented by the insert ring to the frontal part of the cylinder liner. The insulating effect is ensured by a thus formed air gap or the use of ceramics.
- the invention has the object of developing such a cylinder liner in the form that the stability increases in the region of the combustion chamber end of the cylinder liner and sufficient insulation in this area is ensured.
- the cylinder liner collar has a height h B , which is between 65% and 100% or between 83% and 95% or 100% of the height h R of the insert ring.
- the cylinder liner collar is considerably higher and thus stiffer than is the case in the prior art.
- other strength-enhancing measures such as in the groove of the cylinder liner, can be dispensed with.
- an air gap insulation is provided between the insert ring and the cylinder liner, in which at least one defined with respect to the depth air gap is provided with a Gatician 1 L , wherein the ratio of the height h R of the insert ring to the total length 1 L between 1.2 and 1.9 or between 1.5 and 1.7.
- the higher temperatures occurring in the cylinder combustion chamber due to the insulation can be at least partially absorbed by an intensification of the cooling, in particular in the region of the cylinder head and other measures, for example by an adapted coordination of the combustion, so that, for example, with regard to exhaust emissions and fuel consumption Disadvantages arise.
- the total length l L of the air gap results when using several separate air gaps in the form of several wells as explained below from the sum of the heights h v of the depressions.
- the air gap is formed as a recessed into the outer circumference of the insert ring depression or as a recessed into the inner circumference of the recess recess.
- the circumferential recess results from appropriate material withdrawal.
- combined embodiments so for example in the outer periphery of the insert ring and the inner circumference of the recess recesses arranged, be provided, it being important to ensure that on the one hand a good insulation effect is achieved, on the other hand, the insert ring sufficiently stable and solid is held in the cylinder liner.
- the depression is arranged coaxially with the insert ring.
- a decentralized arrangement is also possible such that the depth of the depression varies over the circumference.
- the recess has a height h R and before and after the recess, a web is provided which limits the height h v of the recess.
- a web is provided which limits the height h v of the recess.
- the ratio of the height h v of the depression to the distance a is between 1 and 7 or between 3 and 6 or 4.5. According to the desired insulating effect on the one hand and the necessary rigidity of the insert ring on the other hand, the above ratio should be selected.
- the insert ring has a thickness d R and the recess has a depth t v , wherein the ratio of the thickness d R to the depth t v between 2 and 15 or between 7 and 13.
- the above ratio can be selected taking into consideration the rigidity of the insert ring on the one hand and the insulating effect on the other hand.
- the insulation by an additional insulating ring between the insert ring and the Cylinder liner be formed.
- an additional insulating ring for this purpose, for example, a ceramic material in question.
- the advantage of an additional ring is achieved in the additional support achieved by the insert ring in the cylinder liner by omitting the wells.
- the insert ring lies flat against the insulating ring and is supported against it.
- the cylinder liner is still further stiffened overall.
- Fig. 1 shows a sectional view of the combustion chamber end of a cylinder liner 1 a particular gas-powered internal combustion engine.
- the cylinder liner 1 has a Zylinderbüchsenbund 2, between a cylinder head 3 and a housing 4, in particular a crankcase of the internal combustion engine, is clamped.
- a cylinder head gasket 5 is provided between these components, which is arranged so that no tension of the cylinder liner collar 2 occurs.
- a water jacket 6 is arranged, which is charged with cooling water and extends below the Zylinderbüchsenbundes 2.
- a recess 7 is incorporated on the side facing the cylinder head 3, which extends from the cylinder head end of the cylinder liner 1 into a region below the housing-side end of the cylinder liner collar 2.
- an insert ring 8 is inserted, which is preferably made of the same material as the cylinder liner 1, for example, cast iron.
- the insert ring 8 has on its outer circumference on an air gap insulation, which are embedded in the embodiment in the form of three annular circumferential recesses 9 in the insert ring 8.
- the insert ring 8 preferably has an inner diameter which is slightly smaller than that of the cylinder liner 1 in the region below the recess 7.
- This board of the insert ring 8 causes both on the immersed in the insert ring 8 10th Landstill 10.1 piston adhering carbon and the oil adhering to the insert ring 8 is scraped off by an axial movement direction K of the piston 10.
- the immersion depth of the piston 10 in the insert ring 8 is designed so that an inserted into an upper piston ring groove 11 piston ring 12 at the top dead center (TDC position) of the piston 10 in the cylinder liner 1 just does not come into contact with the insert ring 8.
- the thickness of the insert ring 8 is preferably in the range of 10% to 15% of the total thickness of the cylinder liner collar 2 including the thickness of the recess 7.
- the rings of the insert ring 8 are larger by about 20% than the height of the cylinder liner collar second
- the embodiment according to Fig. 2 differs from the according to Fig. 1 in that recesses 9a embedded in the recess 7 of the cylinder liner 1, for example, are screwed.
- the depressions 9, 9 a have a depth t v in both embodiments, wherein the ratio of a thickness d R of the insert ring 8 to the depth t v is at least 5, ie the depth t v is up to 20% of the thickness d R of Insert ring 8 on.
- the three recesses 9, 9a are arranged at a distance a from each other and separated by two inner webs 14, 14a, wherein the two outer webs 14, 14a form the upper and lower axial end.
- the ratio of a height h v of the respective recess 9, 9a to the distance a is about 4.
- the air gap formed by the recesses 9, 9a has an overall length 1 L.
- the total length 1 L results according to Fig. 4 from a height h R of the insert ring 8 minus the total length of all the webs 14, 14 a, which corresponds to four times the distance a.
- the ratio of the height h R of the insert ring 8 to the total length 1 L is 1.33, ie the total length 1 L is 75% of the height h R of the insert ring. 8
- an additional insulating ring 13 is provided, which is arranged between the insert ring 8 and the cylinder liner collar 2.
- the insert ring 8 lies fully against the insulating ring 13 at.
- the insulating ring 13 is fully against the cylinder liner collar 2.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Description
Die Erfindung betrifft eine Zylinderbüchse für eine Brennkraftmaschine, insbesondere für einen Gasmotor, mit einem Kurbelgehäuse, in dem eine Kurbelwelle drehbar gelagert ist, an der zumindest ein einen Kolben tragendes Pleuel angelenkt ist, wobei in der Zylinderbüchse ein Kolben zwischen einem unteren und einem oberen Totpunkt in eine axiale Richtung K bewegbar ist, wobei die Zylinderbüchse einen Zylinderbüchsenbund aufweist, über den die Zylinderbüchse in einem Gehäuse der Brennkraftmaschine eingesetzt bzw. fixiert ist, und wobei eine zylinderkopfseitige Ausnehmung vorgesehen ist, in der ein Einsatzring mit einer Höhe hR eingesetzt ist.The invention relates to a cylinder liner for an internal combustion engine, in particular for a gas engine, with a crankcase in which a crankshaft is rotatably mounted on which at least one connecting rod carrying a piston is articulated, wherein in the cylinder liner, a piston between a lower and a top dead center in an axial direction K is movable, wherein the cylinder liner has a cylinder liner collar through which the cylinder liner is inserted or fixed in a housing of the internal combustion engine, and wherein a cylinder head side recess is provided, in which an insert ring with a height h R is inserted.
Der Einsatzring ist in der Regel so ausgebildet und angeordnet, dass eine oberste, in den Kolben eingelassene Kolbenringnut bei der OT-Stellung des Kolbens bis an den Einsatzring ragt.The insert ring is usually designed and arranged so that a top, recessed into the piston piston ring groove projects at the TDC position of the piston to the insert ring.
Eine derartige Zylinderbüchse für eine Brennkraftmaschine ist aus der
In der
Der Erfindung liegt die Aufgabe zugrunde, eine derartige Zylinderbüchse in der Form weiterzubilden, dass die Stabilität im Bereich des brennraumseitigen Endes der Zylinderbüchse erhöht und eine ausreichende Isolierung in diesem Bereich gewährleistet wird.The invention has the object of developing such a cylinder liner in the form that the stability increases in the region of the combustion chamber end of the cylinder liner and sufficient insulation in this area is ensured.
Diese Aufgabe wird dadurch gelöst, dass der Zylinderbüchsenbund eine Höhe hB aufweist, die zwischen 65 % und 100 % oder zwischen 83 % und 95 % oder 100 % der Höhe hR des Einsatzrings beträgt. Dadurch ist der Zylinderbüchsenbund erheblich höher und damit steifer ausgebildet, als dies bei dem Stand der Technik der Fall ist. Somit kann dann auf sonstige festigkeitssteigernde Maßnahmen, beispielsweise in der Hohlkehle der Zylinderbüchse, verzichtet werden. Es ist zwar bekannt, dass in diesem brennraumseitigen Bereich der Zylinderbüchse hohe thermische Belastungen auftreten. Diesen thermischen Belastungen ist in der Vergangenheit entgegengewirkt worden, indem gerade in diesem Bereich eine intensive Kühlung angestrebt wurde bzw. die Kühlung möglichst nahe an das stirnseitige Ende der Zylinderbüchse heran geführt wurde. Eine solche intensive Kühlung macht es aber erforderlich, diesen Bereich der Zylinderbüchse bzw. den Zylinderbüchsenbund entsprechend filigran auszubilden, wodurch dieser Bereich der Zylinderbüchse, beispielsweise verursacht durch die Gaskräfte in der Zylinderbüchse, verstärkt anfällig gegenüber Verzug ist. Diese Anfälligkeit wird über den Umfang der Zylinderbüchse durch unterschiedliche Wandstärken des umgebenden Kurbelgehäuses oder sonstiger Zwischengehäuse verstärkt. Begünstigt wird das Auftreten von Verzug durch enge Zylinderabstände, die aufgrund des Wunsches nach kurzbauenden Brennkraftmaschinen auftreten oder sich bei Weiterentwicklungen vorhandener Brennkraftmaschinen aufgrund von Bohrungsvergrößerungen einstellen. Diese Probleme werden durch die erfindungsgemäße Ausgestaltung vermieden, wobei für die Realisierung dieser Ausgestaltung zunächst die Erkenntnis nötig war, dass in der Vergangenheit die thermischen Belastungen zu sehr in den Vordergrund gestellt worden sind.This object is achieved in that the cylinder liner collar has a height h B , which is between 65% and 100% or between 83% and 95% or 100% of the height h R of the insert ring. As a result, the cylinder liner collar is considerably higher and thus stiffer than is the case in the prior art. Thus, then other strength-enhancing measures, such as in the groove of the cylinder liner, can be dispensed with. Although it is known that high thermal loads occur in this combustion chamber side area of the cylinder liner. this thermal loads has been counteracted in the past by intensive cooling was sought in this area or the cooling was as close as possible to the front end of the cylinder liner zoom out. However, such intensive cooling makes it necessary to make this area of the cylinder liner or the cylinder liner collar filigree, whereby this area of the cylinder liner, for example caused by the gas forces in the cylinder liner, is more susceptible to distortion. This vulnerability is enhanced over the circumference of the cylinder liner by different wall thicknesses of the surrounding crankcase or other intermediate housing. The occurrence of distortion is favored by tight cylinder spacings that occur due to the desire for short-burning internal combustion engines or adjust in further developments of existing internal combustion engines due to bore enlargements. These problems are avoided by the embodiment according to the invention, wherein for the realization of this embodiment, first the knowledge was necessary that in the past, the thermal loads have been placed too much in the foreground.
In Weiterbildung der Erfindung ist zwischen dem Einsatzring und der Zylinderbüchse eine Luftspaltisolierung vorgesehen, bei der mindestens ein bezüglich der Tiefe definierter Luftspalt mit einer Gasamtlänge 1L vorgesehen ist, wobei das Verhältnis der Höhe hR des Einsatzrings zu der Gesamtlänge 1L zwischen 1,2 und 1,9 oder zwischen 1,5 und 1,7 ist. Dadurch wird in diesem Bereich die Wärmeabfuhr von dem Einsatzring in die Zylinderbüchse deutlich verringert, so dass im Ergebnis dieser Bereich der Zylinderbüchse bzw. der Zylinderbüchsenbund nicht so intensiv gekühlt werden muss. Innerhalb des Zylinderbüchsenbundes sind separate Kühlraumflächen bzw. Kühlkanäle nicht mehr notwendig und die Zylinderbüchse bzw. der Zylinderbüchsenbund kann in diesem Bereich massiver und verwindungssteifer ausgebildet sein. Die durch die Isolierung auftretenden höheren Temperaturen in dem Zylinderbrennraum können durch eine Intensivierung der Kühlung insbesondere im Bereich des Zylinderkopfs und sonstige Maßnahmen, beispielsweise durch eine angepasste Abstimmung der Verbrennung, zumindest teilweise aufgefangen werden, so dass sich zum Beispiel bezüglich der Abgasemissionen und dem Verbrauch keine Nachteile ergeben. Die Gesamtlänge lL des Luftspaltes ergibt sich beim Einsatz mehrerer getrennter Luftspalte in Form mehrerer Vertiefungen wie nachstehend erläutert aus der Summe der Höhen hv der Vertiefungen.In a further development of the invention, an air gap insulation is provided between the insert ring and the cylinder liner, in which at least one defined with respect to the depth air gap is provided with a Gasamtlänge 1 L , wherein the ratio of the height h R of the insert ring to the total length 1 L between 1.2 and 1.9 or between 1.5 and 1.7. As a result, the heat dissipation from the insert ring into the cylinder liner is significantly reduced in this area, so that, as a result, this area of the cylinder liner or cylinder liner collar does not have to be cooled so intensively. Within the Zylinderbüchsenbundes are separate cold storage areas or cooling channels no longer necessary and the cylinder liner or the cylinder liner collar can be formed in this area more solid and torsionally rigid. The higher temperatures occurring in the cylinder combustion chamber due to the insulation can be at least partially absorbed by an intensification of the cooling, in particular in the region of the cylinder head and other measures, for example by an adapted coordination of the combustion, so that, for example, with regard to exhaust emissions and fuel consumption Disadvantages arise. The total length l L of the air gap results when using several separate air gaps in the form of several wells as explained below from the sum of the heights h v of the depressions.
In weiterer Ausgestaltung der Erfindung kann es vorteilhaft sein, wenn der Luftspalt als eine in den Außenumfang des Einsatzrings eingelassene Vertiefung oder als eine in den Innenumfang der Ausnehmung eingelassene Vertiefung ausgebildet ist. Die umlaufende Vertiefung ergibt sich durch entsprechende Materialrücknahme. Selbstverständlich können im Rahmen der Erfindung auch kombinierte Ausgestaltungen, also beispielsweise in den Außenumfang des Einsatzrings und den Innenumfang der Ausnehmung angeordnete Vertiefungen, vorgesehen sein, wobei darauf zu achten ist, dass einerseits eine gute Isolationswirkung erzielt wird, andererseits der Einsatzring ausreichend stabil ausgebildet und fest in der Zylinderbüchse gehalten ist.In a further embodiment of the invention, it may be advantageous if the air gap is formed as a recessed into the outer circumference of the insert ring depression or as a recessed into the inner circumference of the recess recess. The circumferential recess results from appropriate material withdrawal. Of course, in the context of the invention, combined embodiments, so for example in the outer periphery of the insert ring and the inner circumference of the recess recesses arranged, be provided, it being important to ensure that on the one hand a good insulation effect is achieved, on the other hand, the insert ring sufficiently stable and solid is held in the cylinder liner.
Zudem kann es vorteilhaft sein, wenn die Vertiefung koaxial zu dem Einsatzring angeordnet ist. Anstatt der koaxialen Ausrichtung ist auch eine dezentrische Anordnung derart möglich, dass die Tiefe der Vertiefung über den Umfang variiert.In addition, it may be advantageous if the depression is arranged coaxially with the insert ring. Instead of the coaxial alignment, a decentralized arrangement is also possible such that the depth of the depression varies over the circumference.
Vorteilhaft kann es auch sein, wenn zwei, drei oder mehr Vertiefungen vorgesehen sind, die mit Bezug zur Bewegungsrichtung K übereinander und mit einem Abstand a zueinander angeordnet sind. Somit wird die Isolierwirkung erhöht und dennoch die Steifigkeit des Einsatzrings gewährleistet.It can also be advantageous if two, three or more depressions are provided which are arranged one above the other with respect to the direction of movement K and at a distance a from one another. Thus, the insulating effect is increased and yet ensures the rigidity of the insert ring.
Daneben kann es vorgesehen sein, dass mit Bezug zur axialen Bewegungsrichtung K die Vertiefung einer Höhe hR aufweist und vor und nach der Vertiefung ein Steg vorgesehen ist, der die Höhe hv der Vertiefung begrenzt. Über den Steg bzw. die Stege ist der Einsatzring in der Ausnehmung gegen den Zylinderbüchsenbund abgestützt. Dies hat unmittelbar Einfluss auf die Steifigkeit des Einsatzrings in radialer Richtung. Ferner schottet der Weg die Vertiefungen gegeneinander ab.In addition, it may be provided that, with respect to the axial direction of movement K, the recess has a height h R and before and after the recess, a web is provided which limits the height h v of the recess. About the web or webs of the insert ring is supported in the recess against the cylinder liner collar. This has a direct influence on the rigidity of the insert ring in the radial direction. Furthermore, the path seals the wells against each other.
Hierbei kann es vorteilhaft sein, wenn das Verhältnis der Höhe hv der Vertiefung zu dem Abstand a zwischen 1 und 7 oder zwischen 3 und 6 oder 4,5 ist. Entsprechend der gewünschten Isolierwirkung einerseits sowie der notwendigen Steifigkeit des Einsatzrings andererseits ist das vorstehende Verhältnis zu wählen.In this case, it may be advantageous if the ratio of the height h v of the depression to the distance a is between 1 and 7 or between 3 and 6 or 4.5. According to the desired insulating effect on the one hand and the necessary rigidity of the insert ring on the other hand, the above ratio should be selected.
In diesem Zusammenhang kann es von Vorteil sein, wenn der Einsatzring eine Dicke dR und die Vertiefung eine Tiefe tv aufweist, wobei das Verhältnis von der Dicke dR zu der Tiefe tv zwischen 2 und 15 oder zwischen 7 und 13 ist. Mit der Gewährleistung eines Luftspaltes ist der Wärmeübergang maßgeblich reduziert. Das vorstehend genannte Verhältnis kann unter Berücksichtigung der Steifigkeit des Einsatzrings einerseits sowie der Isolierwirkung andererseits gewählt werden.In this context, it may be advantageous if the insert ring has a thickness d R and the recess has a depth t v , wherein the ratio of the thickness d R to the depth t v between 2 and 15 or between 7 and 13. With the guarantee of an air gap, the heat transfer is significantly reduced. The above ratio can be selected taking into consideration the rigidity of the insert ring on the one hand and the insulating effect on the other hand.
In weiterer Ausgestaltung kann die Isolierung durch einen zusätzlichen Isolierring zwischen dem Einsatzring und der Zylinderbüchse gebildet sein. Hierzu kommt beispielsweise ein Keramikmaterial in Frage. Der Vorteil eines zusätzlichen Ringes besteht in der dadurch erreichten zusätzlichen Abstützung des Einsatzrings in der Zylinderbüchse durch Auslassung der Vertiefungen. Der Einsatzring liegt flächig gegen den Isolierring an und stützt sich gegen diesen ab. Die Zylinderbüchse ist insgesamt noch zusätzlich weiter versteift.In a further embodiment, the insulation by an additional insulating ring between the insert ring and the Cylinder liner be formed. For this purpose, for example, a ceramic material in question. The advantage of an additional ring is achieved in the additional support achieved by the insert ring in the cylinder liner by omitting the wells. The insert ring lies flat against the insulating ring and is supported against it. The cylinder liner is still further stiffened overall.
Gelöst wird die Aufgabe auch durch eine Brennkraftmaschine mit einer vorstehend beschriebenen Zylinderbüchse.The problem is solved by an internal combustion engine with a cylinder liner described above.
Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Zeichnungsbeschreibung zu entnehmen, in der in der Zeichnung dargestellte Ausführungsbeispiele der Erfindung näher beschrieben sind. Es zeigen:
- Figur 1
- eine Schnittdarstellung des brennraumseitigen Endes einer Zylinderbüchse mit in die Zylinderbüchse eingelassener Luftspaltisolierung;
Figur 2- eine Schnittdarstellung des brennraumseitigen Endes einer Zylinderbüchse mit in die Zylinderbüchse eingelassener Luftspaltisolierung mit in den Einsatzring eingelassener Luftspaltisolierung;
Figur 3- eine Schnittdarstellung nach
Fig. 1 mit separatem Isolierring; Figur 4- eine Skizze zur Ermittlung der Gesamtlänge 1L des Luftspaltes.
- FIG. 1
- a sectional view of the combustion chamber-side end of a cylinder liner with embedded in the cylinder liner air gap insulation;
- FIG. 2
- a sectional view of the combustion chamber end of a cylinder liner with let into the cylinder liner air gap insulation with embedded in the insert ring air gap insulation;
- FIG. 3
- a sectional view to
Fig. 1 with separate insulating ring; - FIG. 4
- a sketch to determine the total length 1 L of the air gap.
In die Zylinderbüchse 2 ist auf der dem Zylinderkopf 3 zugewandten Seite eine Ausnehmung 7 eingearbeitet, die sich von dem zylinderkopfseitigen Ende der Zylinderbüchse 1 bis in einen Bereich unterhalb des gehäuseseitigen Endes des Zylinderbüchsenbundes 2 erstreckt. In diese Ausnehmung 7 ist ein Einsatzring 8 eingelassen, der vorzugsweise aus dem gleichen Material wie die Zylinderbüchse 1, beispielsweise Gusseisen, hergestellt ist. Der Einsatzring 8 weist an seinem Außenumfang eine Luftspaltisolierung auf, die im Ausführungsbeispiel in Form von drei ringförmigen umlaufenden Vertiefungen 9 in den Einsatzring 8 eingelassen sind. Der Einsatzring 8 weist bevorzugt einen Innendurchmesser auf, der geringfügig kleiner ist als der der Zylinderbüchse 1 in dem Bereich unterhalb der Ausnehmung 7. Dieser Vorstand des Einsatzrings 8 bewirkt, dass sowohl die an dem in den Einsatzring 8 eintauchenden Feuersteg 10.1 eines Kolbens 10 anhaftende Ölkohle sowie die an dem Einsatzring 8 anhaftende Ölkohle durch eine axiale Bewegungsrichtung K des Kolbens 10 abgeschabt wird. Die Eintauchtiefe des Kolbens 10 in den Einsatzring 8 ist so ausgelegt, dass ein in eine obere Kolbenringnut 11 eingesetzter Kolbenring 12 bei der oberen Totpunktlage (OT-Lage) des Kolbens 10 in der Zylinderbüchse 1 gerade nicht mit dem Einsatzring 8 in Berührung gelangt.In the
Die Dicke des Einsatzrings 8 liegt bevorzugt im Bereich von 10 % bis 15 % der Gesamtdicke des Zylinderbüchsenbundes 2 einschließlich der Dicke der Ausnehmung 7. Die Ringe des Einsatzrings 8 sind um ca. 20 % größer als die Höhe des Zylinderbüchsenbundes 2.The thickness of the insert ring 8 is preferably in the range of 10% to 15% of the total thickness of the
Das Ausführungsbeispiel gemäß
Die Vertiefungen 9, 9a weisen in beiden Ausgestaltungen eine Tiefe tv auf, wobei das Verhältnis von einer Dicke dR des Einsatzrings 8 zu der Tiefe tv mindestens 5 ist, d. h. die Tiefe tv weist bis zu 20 % der Dicke dR des Einsatzringes 8 auf.The depressions 9, 9 a have a depth t v in both embodiments, wherein the ratio of a thickness d R of the insert ring 8 to the depth t v is at least 5, ie the depth t v is up to 20% of the thickness d R of Insert ring 8 on.
Die drei Vertiefungen 9, 9a sind mit einem Abstand a zueinander angeordnet und durch zwei innere Stege 14, 14a voneinander getrennt, wobei die beiden äußeren Stege 14, 14a den oberen bzw. unteren axialen Abschluss bilden. Das Verhältnis einer Höhe hv der jeweiligen Vertiefung 9, 9a zu dem Abstand a beträgt etwa 4.The three recesses 9, 9a are arranged at a distance a from each other and separated by two
Der durch die Vertiefungen 9, 9a gebildete Luftspalt weist eine Gesamtlänge 1L auf. Die Gesamtlänge 1L ergibt sich gemäß
Gemäß Ausführungsbeispiel
- 11
- Zylinderbüchsecylinder liner
- 22
- ZylinderbüchsenbundCylinder liner collar
- 33
- Zylinderkopfcylinder head
- 44
- Gehäusecasing
- 55
- ZylinderkopfdichtungCylinder head gasket
- 66
- Wassermantelwater jacket
- 77
- Ausnehmungrecess
- 88th
- Einsatzringinsert ring
- 99
- Vertiefung, LuftspaltDepression, air gap
- 9a9a
- Vertiefung, LuftspaltDepression, air gap
- 1010
- Kolbenpiston
- 10.110.1
- Feuerstegtop land
- 1111
- Kolbenringnutpiston ring
- 1212
- Kolbenringpiston ring
- 1313
- Isolierringinsulating ring
- 1414
- Stegweb
- 14a14a
- Stegweb
- aa
- Abstand der VertiefungenDistance of the recesses
- dR d R
- Dicke des EinsatzringsThickness of the insert ring
- tv t v
- Tiefe der VertiefungDepth of depression
- hB h B
- Höhe des ZylinderbüchsenbundesHeight of Zylinderbüchsenbundes
- hR h R
- Höhe des EinsatzringsHeight of the insert ring
- hv h v
- Höhe der VertiefungHeight of the recess
- KK
- axiale Bewegungsrichtung des Kolbensaxial direction of movement of the piston
- 1L 1 L
- Gasamtlänge des LuftspaltesGasamtlänge of the air gap
Claims (10)
dadurch gekennzeichnet,
dass der Zylinderbüchsenbund (2) eine Höhe hB aufweist, die zwischen 65 % und 100 % oder zwischen 83 % und 95 % oder 100 % der Höhe hR des Einsatzrings (8) beträgt.Cylinder liner (1) for an internal combustion engine, in particular a gas engine, in which a piston (10) between a lower and a top dead center in an axial direction K is movable and which has a cylinder liner collar (2) over which the cylinder liner (1) in a housing (4) of the internal combustion engine is fixable, wherein a cylinder head side recess (7) is provided, in which an insert ring (8) is inserted with a height h R ,
characterized,
in that the cylinder liner collar (2) has a height h B which is between 65% and 100% or between 83% and 95% or 100% of the height h R of the insert ring (8).
dadurch gekennzeichnet,
dass zwischen dem Einsatzring (8) und der Zylinderbüchse (1) eine Luftspaltisolierung vorgesehen ist, bei der mindestens ein definierter Luftspalt (9, 9a) mit einer Gesamtlänge 1L vorgesehen ist, wobei das Verhältnis der Höhe hR des Einsatzrings (8) zu der Gesamtlänge 1L zwischen 1,1 und 1,9 oder zwischen 1,3 und 1,7 ist.Cylinder liner (1) according to claim 1,
characterized,
in that an air gap insulation is provided between the insert ring (8) and the cylinder liner (1), in which at least one defined air gap (9, 9a) with an overall length 1 L is provided, the ratio of the height h R of the insert ring (8) to the total length 1 L is between 1.1 and 1.9 or between 1.3 and 1.7.
dadurch gekennzeichnet,
dass der Luftspalt (9, 9a) als eine in den Außenumfang des Einsatzrings (8) eingelassene Vertiefung (9) ausgebildet ist.Cylinder liner (1) according to claim 2,
characterized,
in that the air gap (9, 9a) is designed as a recess (9) which is embedded in the outer circumference of the insert ring (8).
dadurch gekennzeichnet,
dass der Luftspalt (9, 9a) als eine in den Innenumfang der Ausnehmung (7) eingelassene Vertiefung (9a) ausgebildet ist.Cylinder liner (1) according to claim 2 or 3,
characterized,
in that the air gap (9, 9a) is designed as a recess (9a) embedded in the inner circumference of the recess (7).
dadurch gekennzeichnet,
dass zwei, drei oder mehr Vertiefungen (9, 9a) vorgesehen sind, die in Bewegungsrichtung K übereinander und mit einem Abstand a zueinander angeordnet sind.Cylinder liner (1) according to claim 3 or 4,
characterized,
in that two, three or more depressions (9, 9a) are provided, which are arranged one above the other in the direction of movement K and at a distance a from one another.
dadurch gekennzeichnet,
dass mit Bezug zur axialen Bewegungsrichtung K die Vertiefung (9, 9a) eine Höhe hv aufweist und vor und nach der Vertiefung (9, 9a) ein Steg (14, 14a) vorgesehen ist, der die Höhe hv der Vertiefung (9, 9a) begrenzt.Cylinder liner (1) according to claim 3, 4 or 5,
characterized,
in that, with respect to the axial movement direction K, the depression (9, 9a) has a height h v and before and after the depression (9, 9a) a web (14, 14a) is provided which determines the height h v of the depression (9, 9a) limited.
dadurch gekennzeichnet,
dass das Verhältnis der Höhe hv der Vertiefung (9, 9a) zu dem Abstand a zwischen 1 und 7 oder zwischen 3 und 6 oder 4,5 ist.Cylinder liner (1) according to claim 5 or 6,
characterized,
that the ratio of the height (9, 9a) is h v of the depression to the distance a 1-7 or 3-6 or 4.5.
dadurch gekennzeichnet,
dass der Einsatzring (8) eine Dicke dR und die Vertiefung (9, 9a) eine Tiefe tv aufweist, wobei das Verhältnis von der Dicke dR zu der Tiefe tv zwischen 3 und 15 oder zwischen 7 und 13 ist.Cylinder liner (1) according to one of the preceding claims,
characterized,
in that the insert ring (8) has a thickness d R and the depression (9, 9a) has a depth t v , the ratio of the thickness d R to the depth t v being between 3 and 15 or between 7 and 13.
dadurch gekennzeichnet,
dass als Isolierung ein zusätzlicher Isolierring (13) vorgesehen ist.Cylinder liner (1) according to one of the preceding claims,
characterized,
in that an additional insulating ring (13) is provided as insulation.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007007977A DE102007007977A1 (en) | 2007-02-17 | 2007-02-17 | Air gap insulation on a cylinder liner |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1965068A1 true EP1965068A1 (en) | 2008-09-03 |
EP1965068B1 EP1965068B1 (en) | 2012-03-14 |
Family
ID=39420683
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08151490A Not-in-force EP1965068B1 (en) | 2007-02-17 | 2008-02-15 | Air gap insulation on a cylinder socket |
Country Status (5)
Country | Link |
---|---|
US (1) | US7726267B2 (en) |
EP (1) | EP1965068B1 (en) |
AT (1) | ATE549500T1 (en) |
DE (1) | DE102007007977A1 (en) |
ES (1) | ES2384192T3 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT519790A1 (en) * | 2017-04-13 | 2018-10-15 | Avl List Gmbh | Internal combustion engine |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9292020B2 (en) | 2009-05-11 | 2016-03-22 | Darrel R. Sand | Fail safe engine coolant thermostat |
US8413632B2 (en) * | 2009-06-04 | 2013-04-09 | Darrel Sand | Zero ridge cylinder bore |
EP2604835B1 (en) * | 2011-12-16 | 2016-04-13 | Caterpillar Motoren GmbH & Co. KG | Cylinder liner and cylinder head for internal combustion engine |
US20160097340A1 (en) * | 2014-10-03 | 2016-04-07 | Caterpillar Inc. | Cylinder liner assembly having air gap insulation |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3038235A1 (en) | 1980-10-10 | 1982-05-06 | Mahle Gmbh, 7000 Stuttgart | Cylinder insert for IC engine - has ribbed outer face to give freedom of movement to improve anti-coking action |
SU1390410A1 (en) | 1986-01-07 | 1988-04-23 | Завод транспортного машиностроения им.В.И.Ленина | Cylinder-piston group |
GB2204658A (en) * | 1987-05-16 | 1988-11-16 | Ae Plc | Cylinder liners |
WO2004022960A1 (en) | 2002-09-05 | 2004-03-18 | Innogy Plc | A cylinder for an internal combustion engine |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2572392A (en) * | 1947-04-23 | 1951-10-23 | Caterpillar Tractor Co | Engine cooling, cylinder jacket, and head construction |
DE1234095B (en) | 1960-07-06 | 1967-02-09 | Sulzer Ag | Fluid-cooled cylinder liner of a piston internal combustion engine |
GB968342A (en) | 1961-03-01 | 1964-09-02 | Ruston & Hornsby Ltd | Improvements in internal combustion engine cylinder heads |
US3489130A (en) | 1968-01-10 | 1970-01-13 | Sealed Power Corp | Piston and cylinder construction |
DE2752633A1 (en) * | 1977-11-25 | 1979-05-31 | Kloeckner Humboldt Deutz Ag | CYLINDER FOR A RECEPTACLE COMBUSTION MACHINE |
DE3236185A1 (en) * | 1982-09-30 | 1984-04-05 | Klöckner-Humboldt-Deutz AG, 5000 Köln | PISTON PISTON ENGINE |
DE19917707C2 (en) * | 1999-04-20 | 2001-03-01 | Daimler Chrysler Ag | Internal combustion engine with a crankcase |
-
2007
- 2007-02-17 DE DE102007007977A patent/DE102007007977A1/en not_active Ceased
-
2008
- 2008-02-15 US US12/070,241 patent/US7726267B2/en active Active
- 2008-02-15 EP EP08151490A patent/EP1965068B1/en not_active Not-in-force
- 2008-02-15 AT AT08151490T patent/ATE549500T1/en active
- 2008-02-15 ES ES08151490T patent/ES2384192T3/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3038235A1 (en) | 1980-10-10 | 1982-05-06 | Mahle Gmbh, 7000 Stuttgart | Cylinder insert for IC engine - has ribbed outer face to give freedom of movement to improve anti-coking action |
SU1390410A1 (en) | 1986-01-07 | 1988-04-23 | Завод транспортного машиностроения им.В.И.Ленина | Cylinder-piston group |
GB2204658A (en) * | 1987-05-16 | 1988-11-16 | Ae Plc | Cylinder liners |
WO2004022960A1 (en) | 2002-09-05 | 2004-03-18 | Innogy Plc | A cylinder for an internal combustion engine |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT519790A1 (en) * | 2017-04-13 | 2018-10-15 | Avl List Gmbh | Internal combustion engine |
AT519790B1 (en) * | 2017-04-13 | 2019-01-15 | Avl List Gmbh | Internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
ATE549500T1 (en) | 2012-03-15 |
US20080196686A1 (en) | 2008-08-21 |
US7726267B2 (en) | 2010-06-01 |
DE102007007977A1 (en) | 2008-08-21 |
ES2384192T3 (en) | 2012-07-02 |
EP1965068B1 (en) | 2012-03-14 |
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