EP0167648B1 - Sealing arrangement - Google Patents

Sealing arrangement Download PDF

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Publication number
EP0167648B1
EP0167648B1 EP19840108101 EP84108101A EP0167648B1 EP 0167648 B1 EP0167648 B1 EP 0167648B1 EP 19840108101 EP19840108101 EP 19840108101 EP 84108101 A EP84108101 A EP 84108101A EP 0167648 B1 EP0167648 B1 EP 0167648B1
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EP
European Patent Office
Prior art keywords
sealing body
rotary valve
sealing
valve member
combustion chamber
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
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EP19840108101
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German (de)
French (fr)
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EP0167648A1 (en
Inventor
Alfred Geissler
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Individual
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Individual
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Publication date
Priority to DE19833300973 priority Critical patent/DE3300973C2/en
Application filed by Individual filed Critical Individual
Priority to AT84108101T priority patent/ATE26475T1/en
Priority to DE8484108101T priority patent/DE3463071D1/en
Priority to EP19840108101 priority patent/EP0167648B1/en
Publication of EP0167648A1 publication Critical patent/EP0167648A1/en
Application granted granted Critical
Publication of EP0167648B1 publication Critical patent/EP0167648B1/en
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/028—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves having the rotational axis coaxial with the cylinder axis and the valve surface not surrounding piston or cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/16—Sealing or packing arrangements specially therefor

Definitions

  • the invention relates to a sealing arrangement for a rotary valve arranged in the combustion chamber of an internal combustion engine, which opens and closes the inlet and outlet openings of gas channels in the cylinder head for the gas exchange, each having a cylindrical sealing body which can be displaced axially in the gas channels of the cylinder head and which can be rotated about its axis has a surface facing away from the rotary valve, between which and an adjacent surface of the cylinder an annular gap is formed which is in permanent communication with the combustion chamber, the combustion chamber gas pressure acting on the surface of the sealing body facing away from the rotary valve, the sealing body with a resulting force against the rotary valve presses.
  • Such a sealing arrangement is known from CH-A-223 378.
  • the sealing body lies in the cylinder and is under high thermal stress, especially since the sealing body is constantly subjected to hot gas during the compression and working stroke.
  • the service life of the sealing body on the one hand and its sealing effect on the other hand are therefore only limited.
  • a similar sealing arrangement is known from DE-C-758 968, in which the sealing body is held on the inside surface of an approximately hollow spherical rotary valve by gas pressure in the combustion chamber.
  • the ring-shaped sealing body is rotatable, but it is flushed with hot fuel gases so that it cannot seal permanently due to heat distortion and the formation of coal.
  • US-A-2 282 594 shows another seal arrangement.
  • the sealing body is assigned to the much cooler cylinder head and the sealing body is only in. the exhaust phase in connection with the combustion chamber. Fuel gases can only reach the sealing body during this short exhaust phase, which would benefit the life of the sealing body.
  • this known proposal has the decisive disadvantage that the sealing body is pressed against the rotary valve by means of a mechanical spring.
  • the spring force must be selected according to the maximum gas pressure in the combustion chamber. For most of the work cycle, the contact pressure is far too high and this leads to rapid wear of the sealing body and thus only to a very limited service life.
  • the sealing body is not rotatable but only axially displaceable. Even due to the heat fluctuations, a uniform all-round seal is no longer available, at least after a certain operating time.
  • US-A-1 354 539 shows an even more disadvantageous solution in that only a spring-loaded sealing body is also used and gas pressure is not present.
  • the sealing body is arranged on the combustion chamber side of the rotary valve, so that this solution has the disadvantages of both known categories.
  • the object of the invention is to arrange the sealing body of the type mentioned with constantly pressurized gas pressure of the combustion chamber while maintaining its sealing function so that it is better protected against heat in order to increase the service life.
  • This object is achieved in that the sealing body rests on the rotary valve surface facing away from the combustion chamber on the rotary valve and that the annular gap communicates with the combustion chamber via a channel lying outside the outer circumference of the sealing body.
  • the new sealing arrangement combines the advantages of the inner arrangement and the outer arrangement of the sealing body with respect to the rotary valve, without having their disadvantages.
  • the sealing body is assigned to the cylinder head, so it is protected from the combustion chamber by the rotary valve during most of the working cycle.
  • the sealing body is exposed to much less heat and therefore lasts much longer. Nevertheless, thanks to the fact that the sealing body is acted upon by the combustion chamber pressure, it is ensured that only the contact pressure which is currently required is provided depending on the instantaneous combustion chamber pressure.
  • a spherical rotary slide 12 is rotatably mounted coaxially to the cylinder axis and is driven by the crankshaft (not shown) via a connecting shaft 14 and two gear wheels 16, 18.
  • the rotary slide valve 12 has a gas channel 20 which opens and closes the inlet channel 22 and the outlet channel 24 in succession.
  • the combustion chamber is designated 26.
  • Sealing body 28 is rotatably mounted about the gas channel axes 30.
  • Each sealing body has a cylindrical wall 32 and an end sealing surface 34 which is designed as a spherical cap ring surface corresponding to the outer surface of the rotary valve 12.
  • the gas channel 22 has an enlarged section 36, in which the peripheral wall 32 is received with axial play and slight radial play.
  • Outer ring grooves 38 in the peripheral wall 32 of the sealing body 28 accommodate sealing rings 40 which seal the gas channel 22 with respect to the combustion chamber.
  • the peripheral wall 32 of the sealing body 28 On the face side, the peripheral wall 32 of the sealing body 28 has an outer collar 42, the outer diameter of which is larger than the inner diameter of the section 36 of the gas channel 22.
  • the outer collar 42 lies face-to-face on the rotary valve 12 and is held in place by a very soft spring 44 even when there is no gas pressure.
  • the spring 44 is accommodated in an annular groove 46 in the cylinder head 10, is supported on the groove bottom and presses on the rear end face of the peripheral wall 32 of the sealing body 28.
  • the bore section 36 of the channel 22 is widened in the region of the outlet opening at 48 in order to accommodate the outer collar 42 of the sealing body 28 with radial play.
  • a circumferential gap 50 is formed between the inner circumferential surface of the area 48 and the outer circumferential surface of the collar 42 and communicates continuously with the combustion chamber 26.
  • This circumferential gap 50 is also connected to a radial annular gap 52 which is formed between a rear surface 54 of the collar 42 of the sealing body 28 facing away from the rotary valve 12 and the combustion chamber 26 and the opposite surface 56 of the cylinder head 10. The rear surface 54 is thus acted upon by the gas pressure in the combustion chamber 26.
  • FIG. 4 shows a cylinder head 11 in which a rotary slide valve 13 is mounted, which instead of a spherical one has a flat sealing surface.
  • the gas channels 22 open in the cylinder head axially parallel to the cylinder axis.
  • the associated sealing body 28 according to FIG. 5 in the inlet duct 22 and in the outlet duct (not shown) differs from that according to FIG. 3 only in that the sealing surface 35 is flat.
  • FIG. 6 shows a sealing body 29 without an outer collar 42. It consists of a circular cylindrical hollow body which is rotatably and axially displaceably inserted in a cylindrical section 37 of the gas channel 22 which is enlarged in diameter.
  • annular groove 58 is formed which is opposite an annular groove 60 corresponding in the opposite surface 56 of the cylinder head 11.
  • a cylindrical sealing ring in the form of a band-shaped web 61 engages with its two opposite ends in the ring grooves 58, 60.
  • the rear end face 54 of the sealing body 29 which adjoins the sealing ring 61 on the outside forms the effective surface under gas pressure for pressing the sealing body onto the rotary slide valve.
  • the sealing body 29 has a small radial distance from the channel section 37 of the cylinder head 11, as a result of which the peripheral gap 50 is formed, which connects the combustion chamber to the annular gap 52.
  • the cylinder head 11 has an annular recess 62 surrounding the gas channel 22, which is only open to the combustion chamber.
  • a sealing body 29 ' is in turn rotatably received with axial play.
  • the axial length of the sealing body 29 ' is somewhat smaller than the length of the annular recess 62.
  • the annular gap 52 acted upon by gas pressure is effective over the entire rear end face of the sealing body 29' facing away from the rotary valve.
  • the sealing body 29 ′ is protected by a peripheral wall 64 facing the gas channel 22. This version is particularly advantageous for the outlet duct.
  • peripheral wall 64 Provided in the peripheral wall 64 are two peripheral grooves 66 which are open toward the annular recess 62 and in which sealing rings 40 are arranged which bear against the inner surface of the sealing body 29 '. Between the outer surface of the sealing body 29 ′ and the adjacent outer peripheral surface of the annular recess 62, a peripheral gap is again formed, which feeds the annular gap 52 with the gas pressure of the combustion chamber 26.
  • FIGS. 6 and 7 can also be used in connection with the spherical rotary slide valve 12 according to FIG. 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Taps Or Cocks (AREA)

Description

Die Erfindung betrifft eine Dichtungsanordnung für einen im Brennraum einer Brenkraftmaschine angeordneten Drehschieber, der Ein- und Auslaßöffnungen von Gaskanälen im Zylinderkopf für den Gaswechsel auf- und zusteuert, mit je einem in den Gaskanälen des Zylinderkopfes axial verschiebbaren zylindrischen, um seine Achse drehbaren Dichtkörper, der eine vom Drehschieber abgewandte Fläche aufweist, zwischen der und einer benachbarten Fläche des Zylinders ein mit dem Brennraum in dauernder Verbindung stehender Ringspalt gebildet ist, wobei der auf die vom Drehschieber abgewandte Fläche des Dichtkörpers wirkende Brennraum-Gasdruck den Dichtkörper mit einer resultierenden Kraft gegen den Drehschieber drückt.The invention relates to a sealing arrangement for a rotary valve arranged in the combustion chamber of an internal combustion engine, which opens and closes the inlet and outlet openings of gas channels in the cylinder head for the gas exchange, each having a cylindrical sealing body which can be displaced axially in the gas channels of the cylinder head and which can be rotated about its axis has a surface facing away from the rotary valve, between which and an adjacent surface of the cylinder an annular gap is formed which is in permanent communication with the combustion chamber, the combustion chamber gas pressure acting on the surface of the sealing body facing away from the rotary valve, the sealing body with a resulting force against the rotary valve presses.

Eine derartige Dichtungsanordnung ist aus der CH-A-223 378 bekannt. Bei ihr liegt der Dichtkörper im Zylinder und steht unter hoher Wärmebelastung, zumal während des Kompressions- und Arbeitshubes der Dichtkörper ständig vom Heißgas beaufschlagt wird. Die Lebensdauer des Dichtkörpers einerseits und seine Dichtwirkung andererseits sind daher nur begrenzt.Such a sealing arrangement is known from CH-A-223 378. With it, the sealing body lies in the cylinder and is under high thermal stress, especially since the sealing body is constantly subjected to hot gas during the compression and working stroke. The service life of the sealing body on the one hand and its sealing effect on the other hand are therefore only limited.

Aus der DE-C-758 968 ist eine ähnliche Dichtungsanordnung bekannt, bei der der Dichtkörper an der Innenfläche eines etwa hohlkugelförmigen Drehschiebers durch Gasdruck im Brennraum in Anage gehalten wird. Auch hier ist der ringförmig ausgebildete Dichtkörper drehbar, jedoch wird er von heißen Brenngasen umspült, so daß er wegen Wärmeverzugs und Olkohlebildung nicht dauerhaft abdichten kann.A similar sealing arrangement is known from DE-C-758 968, in which the sealing body is held on the inside surface of an approximately hollow spherical rotary valve by gas pressure in the combustion chamber. Here too, the ring-shaped sealing body is rotatable, but it is flushed with hot fuel gases so that it cannot seal permanently due to heat distortion and the formation of coal.

Die US-A-2 282 594 zeigt eine andere Dichtungsanordnung. Bei ihr ist der Dichtkörper dem wesentlich kühleren Zylinderkopf zugeordnet und der Dichtkörper steht lediglich in . der Auspuffphase mit dem Brennraum in Verbindung. Brenngase können also nur während dieser kurzen Auspuffphase an den Dichtkörper gelangen, was der Lebensdauer des Dichtkörpers zugute käme. Allerdings weist dieser bekannte Vorschlag den entscheidenden Nachteil auf, daß der Dichtkörper mittels einer mechanischen Feder gegen den Drehschieber gedrückt wird. Die Federkraft muß entsprechend dem maximalen Gasdruck im Brennraum gewählt werden. Für den größten Teil des Arbeitsspiels ist damit die Anpreßkraft viel zu hoch und dies führt zu einer schnellen Abnutzung des Dichtkörpers und damit auch nur zu einer sehr begrenzten Lebensdauer. Der Dichtkörper ist nicht drehbar sondern nur axial verschiebbar. Schon aufgrund der Wärmeschwankungen ist eine gleichmäßige Ringsumabdichtung mindestens nach gewisser Betriebszeit nicht mehr gegeben.US-A-2 282 594 shows another seal arrangement. The sealing body is assigned to the much cooler cylinder head and the sealing body is only in. the exhaust phase in connection with the combustion chamber. Fuel gases can only reach the sealing body during this short exhaust phase, which would benefit the life of the sealing body. However, this known proposal has the decisive disadvantage that the sealing body is pressed against the rotary valve by means of a mechanical spring. The spring force must be selected according to the maximum gas pressure in the combustion chamber. For most of the work cycle, the contact pressure is far too high and this leads to rapid wear of the sealing body and thus only to a very limited service life. The sealing body is not rotatable but only axially displaceable. Even due to the heat fluctuations, a uniform all-round seal is no longer available, at least after a certain operating time.

Die US-A-1 354 539 zeigt eine noch nachteiligere Lösung insofern, daß ebenfalls nur ein federvorgespannter Dichtkörper verwendet wird und eine Gasdruckbeaufschlagung nicht vorhanden ist. Außerdem ist aber der Dichtkörper auf der Brennraumseite des Drehschiebers angeordnet, sodaß diese Lösung die Nachteile beider bekannter Kategorien hat.US-A-1 354 539 shows an even more disadvantageous solution in that only a spring-loaded sealing body is also used and gas pressure is not present. In addition, however, the sealing body is arranged on the combustion chamber side of the rotary valve, so that this solution has the disadvantages of both known categories.

Aufgabe der Erfindung ist es, den Dichtkörper der eingangs genannten Art mit ständig beaufschlagtem Gasdruck des Brennraumes unter Erhaltung seiner Dichtfunktion so anzuordnen, daß er vor Wärmebelastung besser geschützt wird, um die Lebensdauer zu erhöhen.The object of the invention is to arrange the sealing body of the type mentioned with constantly pressurized gas pressure of the combustion chamber while maintaining its sealing function so that it is better protected against heat in order to increase the service life.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der Dichtkörper an der vom Brennraum abgewandten Drehschieberfläche am Drehschieber anliegt und daß der Ringspalt über einen außerhalb des Außenumfanges des Dichtkörpers liegenden Kanal mit dem Brennraum kommuniziert.This object is achieved in that the sealing body rests on the rotary valve surface facing away from the combustion chamber on the rotary valve and that the annular gap communicates with the combustion chamber via a channel lying outside the outer circumference of the sealing body.

Die neue Dichtungsanorndung verbindet die Vorteile der Innenanordnung und der Außenanordnung des Dichtkörpers bezüglich des Drehschiebers, ohne deren Nachteile zu haben. so ist der Dichtkörper dem Zylinderkopf zugeordnet, vom Brennraum also in der allergrößten Zeit des Arbeitsspiels durch den Drehschieber geschützt. Der Dichtkörper wird wesentlich geringer durch Wärme belastet und hält somit auch wesentlich länger. Gleichwohl wird dank der Beaufschlagung des Dichtkörpers durch den Brennraumdruck dafür gesorgt, daß immer nur die gerade notwendige Anpreßkraft in Abhängigkeit vom momentanen Brennraumdruck bereitgestellt wird.The new sealing arrangement combines the advantages of the inner arrangement and the outer arrangement of the sealing body with respect to the rotary valve, without having their disadvantages. the sealing body is assigned to the cylinder head, so it is protected from the combustion chamber by the rotary valve during most of the working cycle. The sealing body is exposed to much less heat and therefore lasts much longer. Nevertheless, thanks to the fact that the sealing body is acted upon by the combustion chamber pressure, it is ensured that only the contact pressure which is currently required is provided depending on the instantaneous combustion chamber pressure.

In den Unteransprüchen sind Weiterbildungen und Ausgestaltungen der Erfindung unter Schutz gestellt.Further developments and refinements of the invention are protected in the subclaims.

Anhand der Zeichnung sei die Erfindung beispielsweise näher erläutert.The invention will be explained in more detail, for example, with reference to the drawing.

Es zeigt:

  • Fig. 1 einen Längsschnitt durch einen Zylinderkopf einer Brennkraftmaschine,
  • Fig. 2 eine Schnittansicht längs der Linie 2-2 der Fig. 1,
  • Fig. 3 eine Schnittansicht des Dichtkörpers in größerem Maßstab,
  • Fig. 4 eine Längsschnittansicht durch einen Zylinderkopf mit ebenem Drehschieber,
  • Fig. 5 eine Schnittansicht durch den Dichtkörper ähnlich Fig. 3, jedoch für den Drehschieber gemäß Fig. 4,
  • Fig. 6 eine Schnittansicht eines abgewandelten Dichtkörpers und
  • Fig. 7 eine Schnittansicht eines weiter abgewandelten Dichtkörpers.
It shows:
  • 1 shows a longitudinal section through a cylinder head of an internal combustion engine,
  • 2 is a sectional view taken along line 2-2 of FIG. 1,
  • 3 is a sectional view of the sealing body on a larger scale,
  • 4 is a longitudinal sectional view through a cylinder head with a flat rotary valve,
  • 5 is a sectional view through the sealing body similar to FIG. 3, but for the rotary valve according to FIG. 4,
  • Fig. 6 is a sectional view of a modified sealing body and
  • Fig. 7 is a sectional view of a further modified sealing body.

Im Zylinderkopf 10 ist ein kugelförmiger Drehschieber 12 koaxial zur Zylinderachse drehbar gelagert und wird von der nicht dargestellten Kurbelwelle über eine Verbindungswelle 14 und zwei Zahnräder 16, 18 angetrieben. Der Drehschieber 12 weist einen Gaskanal 20 auf, der nacheinander den Einlaßkanal 22 und den Auslaßkanal 24 öffnet und schließt. Der Brennraum ist mit 26 bezeichnet. Im Bereich der brennraumseitigen Öffnungen der Gaskanäle 22, 24 sind jeweils ringförmige Dichtkörper 28 um die Gaskanalachsen 30 drehbar gelagert. Jeder Dichtkörper hat eine zylindrische Wand 32 und eine stirnseitige Dichtfläche 34, die entsprechend der Außenfläche des Drehschiebers 12 als Kugelkalotten-Ringfläche ausgebildet ist. Der Gaskanal 22 hat einen erweiterten Abschnitt 36, in dem die Umfangswand 32 mit Axialspiel und geringem Radialspiel aufgenommen ist. Äußere Ringnuten 38 in der Umfangswand 32 des Dichtkörpers 28 nehmen Dichtringe 40 auf, die den Gaskanal 22 gegenüber dem Brennraum abdichten. Stirnseitig weist die Umfangswand 32 des Dichtkörpers 28 einen Außenbund 42 auf, dessen Außendurchmesser größer als der Innendurchmesser des Abschnittes 36 des Gaskanals 22 ist. Der Außenbund 42 liegt stirnseitig ganzflächig am Drehschieber 12 an und wird mittels einer sehr weichen Feder 44 auch bei fehlendem Gasdruck anliegend gehalten. Die Feder 44 ist in einer Ringnut 46 im Zylinderkopf 10 untergebracht, stützt sich am Nutboden ab und drückt auf die rückwärtige Stirnfläche der Umfangswand 32 des Dichtkörpers 28.In the cylinder head 10, a spherical rotary slide 12 is rotatably mounted coaxially to the cylinder axis and is driven by the crankshaft (not shown) via a connecting shaft 14 and two gear wheels 16, 18. The rotary slide valve 12 has a gas channel 20 which opens and closes the inlet channel 22 and the outlet channel 24 in succession. The combustion chamber is designated 26. In the area of the openings of the gas channels 22, 24 on the combustion chamber side, there are ring-shaped openings Sealing body 28 is rotatably mounted about the gas channel axes 30. Each sealing body has a cylindrical wall 32 and an end sealing surface 34 which is designed as a spherical cap ring surface corresponding to the outer surface of the rotary valve 12. The gas channel 22 has an enlarged section 36, in which the peripheral wall 32 is received with axial play and slight radial play. Outer ring grooves 38 in the peripheral wall 32 of the sealing body 28 accommodate sealing rings 40 which seal the gas channel 22 with respect to the combustion chamber. On the face side, the peripheral wall 32 of the sealing body 28 has an outer collar 42, the outer diameter of which is larger than the inner diameter of the section 36 of the gas channel 22. The outer collar 42 lies face-to-face on the rotary valve 12 and is held in place by a very soft spring 44 even when there is no gas pressure. The spring 44 is accommodated in an annular groove 46 in the cylinder head 10, is supported on the groove bottom and presses on the rear end face of the peripheral wall 32 of the sealing body 28.

Der Bohrungsabschnitt 36 des Kanals 22 ist im Bereich der Auslaßöffnung bei 48 verbreitert, um den Außenbund 42 des Dichtkörpers 28 mit Radialspiel aufzunehmen. Zwischen der inneren Umfangsfläche des Bereiches 48 und der äußeren Umfangsfläche des Bundes 42 wird ein Umfangsspalt 50 gebildet, der ständig mit dem Brennraum 26 kommuniziert. Dieser Umfangsspalt 50 steht weiterhin mit einem radialen Ringspalt 52 in Verbindung, der zwischen einer dem Drehschieber 12 und dem Brennraum 26 abgekehrten rückwärtigen Fläche 54 des Bundes 42 des Dichtkörpers 28 und der gegenüberliegenden Fläche 56 des Zylinderkopfes 10 gebildet ist. Die rückwärtige Fläche 54 wird somit vom Gasdruck im Brennraum 26 beaufschlagt. Es ergibt sich eine resultierende Kraft, mit der der Dichtkörper 28 gegen dem Drehschieber 12 gedrückt wird, der gleich ist dem Produkt aus dem jeweiligen Gasdruck und einer Ringfläche, deren Außendurchmesser gleich dem des Bundes 42 und deren Innendurchmesser gleich dem des Gaskanalabschnittes 36 ist.The bore section 36 of the channel 22 is widened in the region of the outlet opening at 48 in order to accommodate the outer collar 42 of the sealing body 28 with radial play. A circumferential gap 50 is formed between the inner circumferential surface of the area 48 and the outer circumferential surface of the collar 42 and communicates continuously with the combustion chamber 26. This circumferential gap 50 is also connected to a radial annular gap 52 which is formed between a rear surface 54 of the collar 42 of the sealing body 28 facing away from the rotary valve 12 and the combustion chamber 26 and the opposite surface 56 of the cylinder head 10. The rear surface 54 is thus acted upon by the gas pressure in the combustion chamber 26. The result is a resultant force with which the sealing body 28 is pressed against the rotary slide valve 12, which is equal to the product of the respective gas pressure and an annular surface, the outer diameter of which is equal to that of the collar 42 and the inner diameter of which is equal to that of the gas channel section 36.

Figur 4 zeigt einen Zylinderkopf 11, in dem ein Drehschieber 13 gelagert ist, der anstelle einer kugelförmigen eine ebene Dichtfläche aufweist. Die Gaskanäle 22 münden im Zylinderkopf achsparallel zur Zylinderachse. Der zugehörige Dichtkörper 28 gemäß Figur 5 im Einlaßkanal 22 und im nicht dargestellten Auslaßkanal unterscheidet sich von dem jenigen gemäß Figur 3 lediglich dadurch, daß die Dichtfläche 35 eben ausgebildet ist.FIG. 4 shows a cylinder head 11 in which a rotary slide valve 13 is mounted, which instead of a spherical one has a flat sealing surface. The gas channels 22 open in the cylinder head axially parallel to the cylinder axis. The associated sealing body 28 according to FIG. 5 in the inlet duct 22 and in the outlet duct (not shown) differs from that according to FIG. 3 only in that the sealing surface 35 is flat.

Figur 6 zeigt einen Dichtkörper 29 ohne Außenbund 42. Er besteht aus einem kreiszylindrischen Hohlkörper, der in einem, im Durchmesser vergrößerten zvlindrischen Abschnitt 37 des Gaskanals 22 drehbar und axial verschiebbar eingesetzt ist. In der vom Drehkörper abgewandten rückwärtigen Stirnfläche 54 des Dichtkörpers 29 ist eine Ringnut 58 ausgebildet, der eine, in der gegenüberliegenden Fläche 56 des Zylinderkopfes 11 entsprechende Ringnut 60 gegenüberliegt. Ein zylindrischer Dichtring in Form eines bandförmigen Steges 61 greift mit seinen beiden gegenüberliegenden stirnseitigen Enden jeweils in die Ringnuten 58, 60 ein. Die sich außen an den Dichtring 61 anschließende rückwärtige Stirnfläche 54 des Dichtkörpers 29 bildet die gasdruck-beaufschlagte wirksame Fiäche zum Andrücken des Dichtkörpers an den Drehschieber. Der Dichtkörper 29 hat einen geringen Radialabstand vom Kanalabschnitt 37 des Zylinderkopfes 11, wodurch der Umfangsspalt 50 gebildet wird, der den Brennraum mit dem Ringspalt 52 verbindet.FIG. 6 shows a sealing body 29 without an outer collar 42. It consists of a circular cylindrical hollow body which is rotatably and axially displaceably inserted in a cylindrical section 37 of the gas channel 22 which is enlarged in diameter. In the rear end face 54 of the sealing body 29 facing away from the rotary body, an annular groove 58 is formed which is opposite an annular groove 60 corresponding in the opposite surface 56 of the cylinder head 11. A cylindrical sealing ring in the form of a band-shaped web 61 engages with its two opposite ends in the ring grooves 58, 60. The rear end face 54 of the sealing body 29 which adjoins the sealing ring 61 on the outside forms the effective surface under gas pressure for pressing the sealing body onto the rotary slide valve. The sealing body 29 has a small radial distance from the channel section 37 of the cylinder head 11, as a result of which the peripheral gap 50 is formed, which connects the combustion chamber to the annular gap 52.

Gemäß Figur 7 hat der Zylinderkopf 11 eine den Gaskanal 22 umgebende ringförmige Aussparung 62, die lediglich zum Brennraum hin offen ist. In dieser Aussparung 62 ist ein Dichtkörper 29' wiederum drehbar mit Axialspiel aufgenommen. Die axiale Länge des Dichtkörpers 29' ist etwas kleiner als die Länge der ringfömrigen Aussparung 62. Der gasdruck-beaufschlagte Ringspalt 52 ist über die gesamte, dem Drehschieber abgewandte rückwärte Stirnfläche des Dichtkörpers 29' wirksam. Der Dichtkörper 29' ist von einer, dem Gaskanal 22 zugewandten Umfangswand 64 geschützt. Diese Ausführung ist insbesondere für den Auslaßkanal vorteilhaft. In der Umfangswand 64 sind zwei, zur ringförmigen Aussparung 62 hin offene Umfangsnuten 66 vorgesehen, in denen Dichtungsringe 40 angeordnet sind, die an der Innenfläche des Dichtkörpers 29' anliegen. Zwischen der Außenfläche des Dichtkörpers 29' und der benachbarten äußeren Umfangsfläche der ringförmigen Aussparung 62 wird wiederum ein Umfangsspalt gebildet, der den Ringspalt 52 mit dem Gasdruck des Brennraumes 26 speist.According to FIG. 7, the cylinder head 11 has an annular recess 62 surrounding the gas channel 22, which is only open to the combustion chamber. In this recess 62, a sealing body 29 'is in turn rotatably received with axial play. The axial length of the sealing body 29 'is somewhat smaller than the length of the annular recess 62. The annular gap 52 acted upon by gas pressure is effective over the entire rear end face of the sealing body 29' facing away from the rotary valve. The sealing body 29 ′ is protected by a peripheral wall 64 facing the gas channel 22. This version is particularly advantageous for the outlet duct. Provided in the peripheral wall 64 are two peripheral grooves 66 which are open toward the annular recess 62 and in which sealing rings 40 are arranged which bear against the inner surface of the sealing body 29 '. Between the outer surface of the sealing body 29 ′ and the adjacent outer peripheral surface of the annular recess 62, a peripheral gap is again formed, which feeds the annular gap 52 with the gas pressure of the combustion chamber 26.

Es versteht sich, daß die Ausführungen gemäß Figuren 6 und 7 auch in Verbindung mit dem kugelförmigen Drehschieber 12 gemäß Figur 1 verwendet werden können.It goes without saying that the designs according to FIGS. 6 and 7 can also be used in connection with the spherical rotary slide valve 12 according to FIG. 1.

Claims (8)

1. A sealing arrangement for a rotary valve member (12; 13) arranged within the combustion chamber of an internal combustion engine, the rotary valve member (12; 13) provided for opening and closing inlet and outlet openings of gas channels (22; 24) provided in the cylinder head (10; 11) for the gas change,comprising a cylindrical sealing body (28; 29; 29') rotatably . arranged about its axis and mounted for axial displacement in each one of the gas channels (22; 24) of the cylinder head (10; 11), the sealing body (28; 29; 29') provided with a surface (54) averted from the rotary valve member (12; 13), an annular gap (52) formed between said averted surface and an adjacent surface (56) of the cylinder, the annular gap (52) being in permanent communication with the combustion chamber (26), whereby the combustion chamber gas pressure acting on the surface (54) of the sealing body (28; 29; 29') averted from the rotary valve member (12; 13) urges the sealing body (28; 29; 29') against the rotary valve member (10; 11) with a resultant force, characterized in that the sealing body (28; 29; 29') contacts the rotary valve member (12; 13) at the rotary valve member surface averted from the combustion chamber (26) and that the annular gap (52) communicates with the combustion chamber (26) via a channel (50) situated outside of the outer periphery of the sealing body (28; 29; 29').
2. A sealing arrangement according to claim 1, characterized in that the sealing body (28; 29; 29') is arranged in an annular recess (36; 37; 62) of the cylinder head (10; 11).
3. A sealing arrangement according to claim 1 or 2, characterized in that the channel (50) is formed as a peripheral gap between the outside periphery of the sealing body (28; 29; 29') and the cylinder head (10; 11).
4. A sealing arrangement according to claim 1 or 2, characterized in that, the annular recess (62) opens exclusively into the combustion chamber (26).
5. A sealing arrangement according to one of the claims 1 to 4, characterized in that a relatively weak mechanical spring (44) is arranged in the cylinder head (10; 11) which urges the sealing body (28; 29; 29') against the rotary valve member (12; 13).
6. A sealing arrangement according to one of the claims 1 to 5, characterized in that the sealing body (28) is provided with an outwardly extending flange (42) contacting the rotary valve member (12; 13), the outside diameter of the flange (42) being greater than the inside diameter of a section (36) of the gas channel (22; 24) in which the sealing body is mounted.
7. A sealing arrangement according to one of the claims 1 to 6, characterized in that the sealing body (29) at its surface (54) averted from the rotary valve member (12; 13) is provided with an annular groove (58) a similar annular groove (60) is formed in a surface (56) of the cylinder head (10; 11) facing said averted surface (54) and that at least one band-shaped sealing ring (61) with both of its opposite frontside ends engages into said annular grooves (58, 60).
8. A sealing arrangement according to one of the claims 2 to 7, characterized in that in a peripheral wall (64) of the cylinder head (10; 11) at least one peripheral groove (66) is provided limiting, the annular recess (62), facing the gas channel (22; 24) and opening into the annular recess (62), and a sealing ring (40) contacting the inner peripheral surface of the sealing body (29') is contained in the peripheral groove (66).
EP19840108101 1983-01-13 1984-07-11 Sealing arrangement Expired EP0167648B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE19833300973 DE3300973C2 (en) 1983-01-13 1983-01-13 Sealing arrangement for a rotary valve of an internal combustion engine
AT84108101T ATE26475T1 (en) 1984-07-11 1984-07-11 SEAL ARRANGEMENT.
DE8484108101T DE3463071D1 (en) 1984-07-11 1984-07-11 Sealing arrangement
EP19840108101 EP0167648B1 (en) 1983-01-13 1984-07-11 Sealing arrangement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19833300973 DE3300973C2 (en) 1983-01-13 1983-01-13 Sealing arrangement for a rotary valve of an internal combustion engine
EP19840108101 EP0167648B1 (en) 1983-01-13 1984-07-11 Sealing arrangement

Publications (2)

Publication Number Publication Date
EP0167648A1 EP0167648A1 (en) 1986-01-15
EP0167648B1 true EP0167648B1 (en) 1987-04-08

Family

ID=25807532

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Application Number Title Priority Date Filing Date
EP19840108101 Expired EP0167648B1 (en) 1983-01-13 1984-07-11 Sealing arrangement

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EP (1) EP0167648B1 (en)
DE (1) DE3300973C2 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3300973C2 (en) * 1983-01-13 1985-08-01 Alfred Dipl.-Ing. Geißler (FH), 8999 Weiler-Simmerberg Sealing arrangement for a rotary valve of an internal combustion engine
DE4410109C2 (en) * 1994-03-21 1997-09-04 Peter Fertig Rotary slide body and device for gas exchange control
GB9820923D0 (en) * 1998-09-28 1998-11-18 Bsa Rocv Limited Improvements in or relating to rotary valves
CN108871784B (en) * 2018-04-27 2020-12-18 北京航天动力研究所 Fixing device for liquid rocket engine thrust chamber airflow test

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1357600A (en) * 1920-11-02 Chakles t
US1354539A (en) * 1919-03-24 1920-10-05 Dickerson Engine Company Port-packing for rotary valves
DE678953C (en) * 1935-06-20 1939-07-26 Argus Motoren Ges M B H Seal for internal combustion engines with a rotating slide or a slide swinging around its central axis in the form of a ball
US2283594A (en) * 1935-07-23 1942-05-19 Aspin Frank Metcalf Internal combustion engine
CH223378A (en) * 1938-05-20 1942-09-15 Versuchsanstalt Fuer Luftfahrt Device on internal combustion engines with a disc-shaped rotary valve for sealing the valve.
DE758968C (en) * 1940-04-17 1954-06-28 Bmw Flugmotorenbau Ges M B H Seal for rotary valve controlled internal combustion engines
DE904959C (en) * 1951-08-28 1954-02-25 Nsu Werke Ag Air-cooled four-stroke combustion engine with rotary valve control
DE3300973C2 (en) * 1983-01-13 1985-08-01 Alfred Dipl.-Ing. Geißler (FH), 8999 Weiler-Simmerberg Sealing arrangement for a rotary valve of an internal combustion engine

Also Published As

Publication number Publication date
DE3300973A1 (en) 1984-07-26
DE3300973C2 (en) 1985-08-01
EP0167648A1 (en) 1986-01-15

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