EP0756068A2 - Rotary internal combustion engine - Google Patents

Rotary internal combustion engine Download PDF

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Publication number
EP0756068A2
EP0756068A2 EP96110913A EP96110913A EP0756068A2 EP 0756068 A2 EP0756068 A2 EP 0756068A2 EP 96110913 A EP96110913 A EP 96110913A EP 96110913 A EP96110913 A EP 96110913A EP 0756068 A2 EP0756068 A2 EP 0756068A2
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EP
European Patent Office
Prior art keywords
piston
internal combustion
combustion engine
sealing ring
ring
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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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EP96110913A
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German (de)
French (fr)
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EP0756068A3 (en
Inventor
Wilfried Ball
Peter Rönnberg
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Individual
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Publication of EP0756068A3 publication Critical patent/EP0756068A3/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/07—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having crankshaft-and-connecting-rod type drive
    • 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
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the invention relates to a rotary piston internal combustion engine according to the preamble of the main claim.
  • Such rotary piston internal combustion engines are provided with a control device which controls the rotary movement of the two piston carriers in such a way that working spaces formed between two different piston carriers belonging to adjacent pistons within the cylinder space are alternately enlarged and reduced during the rotational movement of the pistons and that during the non-uniform rotary movement of the Piston carrier performs a uniform rotary movement.
  • the angular position of the enlarging and reducing spaces relative to the cylinder space is fixed.
  • the cylinder space is provided with at least one inlet opening in the area of an enlarging space and at least one outlet opening in the area of a shrinking space, between which an ignition area is formed in the cylinder space, within which the working spaces circulating between the pistons assume a minimum volume and in them contained ignitable mixture ignites.
  • Such a rotary piston internal combustion engine is known from US Pat. No. 3,890,939.
  • the seal between the housing and the piston carriers is provided by sealing rings, which are each arranged in opposing annular grooves formed in the housing and the adjacent piston carrier or the two piston carriers, and depending on the radial pressure difference on the radially outer or radially inner surfaces of these ring grooves.
  • the seal achieved is heavily dependent on tolerances.
  • the invention has for its object to provide a generic rotary piston internal combustion engine, the cylinder chamber is reliably sealed.
  • a rotary piston internal combustion engine has a housing, designated overall by 2, which consists of a motor housing 4 and a gear housing 6.
  • the motor housing consists of two shells 4a, 4b, which enclose between them an inwardly open annular cylinder space 8, and whose shell 4a is blocked with the transmission housing 2.
  • a total of 4 pistons, not shown in FIG. 1, circulate in the cylinder chamber 8, two of which are fastened diametrically opposite one another to one of two piston carriers 10 and 12.
  • the piston carriers are provided towards the cylinder chamber 8 with such peripheral surfaces that they complement the inner surface of the cylinder chamber to a circular cross-section, the one piston carrier forming a running surface for the pistons not attached to it.
  • the piston carrier 12 is connected in a rotationally fixed manner to a hollow shaft 14 which projects into the gear housing 6 and has a radial arm 16 which is connected to a crankshaft 20 via a connecting rod 18.
  • piston carrier 10 is rigidly attached to a shaft 22 which extends within the hollow shaft 14 into the gear housing 6 and ends in a radial arm 24 which is connected to a crankshaft 28 via a connecting rod 26.
  • crankshafts 26 and 28 are mounted in a crankcase 30 and end in gearwheels 32, 34 connected to them in a rotationally fixed manner, which mesh with a gearwheel 26 fixed to the gearbox housing.
  • the crankcase 30 is rotatable within the gear housing 6 and extends with an output shaft 38 through the gear housing.
  • the number of teeth of the gears 32, 34 and 36 are matched to one another such that the crankshafts 20 and 28 rotate during one revolution of the crankcase 30 Turn twice so that each working space formed between the pistons in the cylinder space 8 increases and decreases twice in the course of a complete revolution, so that a four-stroke working method can be carried out in the presence of an intake duct and an exhaust duct, not shown.
  • FIG. 3 shows a view according to FIG. 1 from the left with the shell 4a partially cut open.
  • the two piston carriers 10 and 12 are visible, the diameter of the piston carrier 12 being shown somewhat enlarged, and one each of the pistons 38 and 40 fastened to the piston carriers.
  • the working space 42 enclosed between the pistons 38 and 40 is just minimal in size and is located in the area of a spark plug 44, which is provided when the internal combustion engine is operating as a gasoline engine.
  • Fig. 4 shows the formation of a mechanical seal, as it can be used at points designated by X in Fig. 1 between two movable components, that is, the housing shell and piston carrier or the two piston carriers.
  • the seal sits between the shell 4a and the piston carrier 10.
  • the shell 4a is provided with an annular groove 46, in which a sealing ring 47, which acts as a sliding ring, is arranged, which over a large area rests against the piston carrier 10 in the annular groove 46.
  • blind holes 48 are distributed over the circumference of the annular groove 46, in each of which a spring 50 is arranged which presses a pin 52 into a recess in the sealing ring 47 . It goes without saying that a pin does not have to be present in each of the blind holes, since the rotation lock is already achieved, for example, with three pins distributed at equal angular intervals.
  • a plurality of springs 50 for example 18, evenly over the circumference of the annular groove 46.
  • the sealing ring 47 is provided with a circumferential annular groove 58, into which two spring rings 60, 62 which act as sealing rings are inserted such that their gaps are mutually rotated, for example, by 180 °.
  • the sealing rings 60, 62 can be held in a rotationally fixed manner by means of suitable means, for example pins or bulges of the base of the annular groove 58.
  • the arrangement of the sealing rings 60, 62 on the radially outer side has the advantage that lubricant coming from the shafts 14, 22 or according to FIG. 4 can penetrate into the gap between the sealing ring 47 and the shell 4a, so that it additionally supports the installation of the sealing ring 47 on the piston carrier 10.
  • the piston carrier 10 is fastened to the shaft 22 via an internal toothing.
  • the piston carrier 10 comprises two spokes 64, of which only the upper spoke with the piston 38 formed in one piece with it is shown.
  • a ring part 66 is attached to the spoke 64, which rotates together with the piston carrier 22 and, together with a corresponding ring part 68 fastened to the other piston carrier, closes off the cylinder space 8 in the direction of the shaft 22.
  • the piston 38 is arranged eccentrically to the cylinder space 8 when the engine is not in the operating state, so that it moves into a central position when heated due to the expansion of its material and the material of the spoke 64.
  • the seal between the piston 38 and the inner wall of the cylinder space 8 is taken over by piston rings 70.
  • the piston carrier 10, 12 consist of a material with a lower coefficient of thermal expansion than the material of the motor housing 4, since the motor housing 4 can be directly water-cooled, whereas the piston carrier are difficult to access for water cooling.
  • the illustrated embodiment of the piston carrier 10 with the spokes 64 and the ring part 66 has the following advantage:

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

The engine housing contains a cylinder chamber with an even number of pistons and a ring groove (46). The sealing ring (47) set in the ring groove of the housing or one of the piston supports is biased by a force acting from the groove and adjoins a counter face of the relevant piston support. A spring (50) can be mounted between the base of the ring groove and the sealing ring. A pin (52) set between a blind hole (48) in the base of the ring groove and a recess of the sealing ring secures the latter against turning. The sealing ring has on its radially outer face a circumferential groove (58) containing a spring ring (60).

Description

Die Erfindung betrifft eine Drehkolben-Brennkraftmaschine gemäß dem Oberbegriff des Hauptanspruchs.The invention relates to a rotary piston internal combustion engine according to the preamble of the main claim.

Solche Drehkolben-Brennkraftmaschinen sind mit einer Steuervorrichtung versehen, die die Drehbewegung der beiden Kolbenträger derart steuert, daß sich zwischen zwei unterschiedlichen Kolbenträgem zugehörenden, benachbarten Kolben innerhalb des Zylinderraums gebildeten Arbeitsräume während der Umlaufbewegung der Kolben abwechselnd vergrößern und verkleinern und die während der ungleichförmigen Drehbewegung der Kolbenträger eine gleichförmige Drehbewegung ausführt. Die Winkellage der sich vergrößernden und verkleinernden Räume relativ zum Zylinderraum liegt fest. Der Zylinderraum ist im Bereich eines sich vergrößernden Raums wenigstens mit einer Einlaßöffnung und im Bereich eines sich verkleinernden Raums wenigstens mit einer Auslaßöffnung versehen, zwischen denen im Zylinderraum ein Zündbereich gebildet ist, innerhalb dessen die zwischen den Kolben umlaufenden Arbeitsräume ein minimales Volumen annehmen und in ihnen enthaltenes zündfähiges Gemisch zündet.Such rotary piston internal combustion engines are provided with a control device which controls the rotary movement of the two piston carriers in such a way that working spaces formed between two different piston carriers belonging to adjacent pistons within the cylinder space are alternately enlarged and reduced during the rotational movement of the pistons and that during the non-uniform rotary movement of the Piston carrier performs a uniform rotary movement. The angular position of the enlarging and reducing spaces relative to the cylinder space is fixed. The cylinder space is provided with at least one inlet opening in the area of an enlarging space and at least one outlet opening in the area of a shrinking space, between which an ignition area is formed in the cylinder space, within which the working spaces circulating between the pistons assume a minimum volume and in them contained ignitable mixture ignites.

Eine solche Drehkolben-Brennkraftmaschine ist aus der US-PS 3,890,939 bekannt. Die Abdichtung zwischen dem Gehäuse und den Kolbenträgern erfolgt bei dieser bekannten Brennkraftmaschine durch Dichtringe, die jeweils in sich gegenüberliegend im Gehäuse und dem benachbarten Kolbenträger bzw. den beiden Kolbenträgern ausgebildeten Ringnuten angeordnet sind und je nach radialer Druckdifferenz an den radial äußeren oder den radial inneren Flächen dieser Ringnuten anliegen. Die erzielte Dichtung ist stark von Toleranzen abhängig.Such a rotary piston internal combustion engine is known from US Pat. No. 3,890,939. In this known internal combustion engine, the seal between the housing and the piston carriers is provided by sealing rings, which are each arranged in opposing annular grooves formed in the housing and the adjacent piston carrier or the two piston carriers, and depending on the radial pressure difference on the radially outer or radially inner surfaces of these ring grooves. The seal achieved is heavily dependent on tolerances.

Der Erfindung liegt die Aufgabe zugrunde, eine gattungsgemäße Drehkolben-Brennkraftmaschine zu schaffen, deren Zylinderraum zuverlässig abgedichtet ist.The invention has for its object to provide a generic rotary piston internal combustion engine, the cylinder chamber is reliably sealed.

Diese Aufgabe wird mit den kennzeichnenden Merkmalen des Hauptanspruchs gelöst. Mit der erfindungsgemäßen Anordnung der Dichtringe und deren Vorspannung in Richtung auf die jeweilige Gegenfläche wird erreicht, daß für jeden Dichtring nur eine Ringnut erforderlich ist und die jeweilige Gegenfläche plan, d.h. ohne Ringnut ausgebildet sein kann, so daß eine weitgehende Unabhängigkeit von Fertigkeitstoleranzen besteht. Der Dichtring kann großflächig an der jeweiligen Gegenfläche anliegen, was die Dichtwirkung verbessert und zusätzlich für eine Wärmeabfuhr sorgt, wenn beispielsweise der Dichtring einseitig Schmiermittel-umspült ist. Dadurch, daß für jeden Dichtring nur eine Ringnut vorgesehen sein muß, ist der Fertigungsaufwand vermindert.This object is achieved with the characterizing features of the main claim. With the arrangement according to the invention of the sealing rings and their prestressing in the direction of the respective counter surface, it is achieved that only one ring groove is required for each sealing ring and the respective counter surface is flat, i.e. can be designed without an annular groove, so that there is a large degree of independence from skill tolerances. The sealing ring can lie on the respective counter surface over a large area, which improves the sealing effect and additionally ensures heat dissipation if, for example, the sealing ring is flushed with lubricant on one side. Because only one annular groove has to be provided for each sealing ring, the manufacturing outlay is reduced.

Die Unteransprüche sind auf vorteilhafte Weiterbildungen der erfindungsgemäßen Drehkolben-Brennkraftmaschine gerichtet.The subclaims are directed to advantageous developments of the rotary piston internal combustion engine according to the invention.

Die Erfindung wird im folgenden anhand schematischer Zeichnungen beispielsweise und mit weiteren Einzelheiten erläutert.The invention is explained below with reference to schematic drawings, for example and with further details.

Es stellen dar:

Fig. 1
einen Längsschnitt durch eine erfindungsgemäße Drehkolben-Brennkraftmaschine,
Fig. 2
eine Ansicht des Kurbelgetriebes von rechts gemäß Fig. 1,
Fig. 3
eine Ansicht der Kolben mit Kolbenträger, gesehen gemäß Fig. 1 von links,
Fig. 4
eine vorteilhafte Ausführungsform einer Abdichtung zwischen zwei beweglichen Teilen.
Fig. 5
eine axiale Ansicht eines Kolbenträgers mit Kolben und
Fig. 6
eine Schnittansicht der Anordnung gemäß Fig. 5, geschnitten längs der Linie VI-VI.
They represent:
Fig. 1
2 shows a longitudinal section through a rotary piston internal combustion engine according to the invention,
Fig. 2
2 shows a view of the crank mechanism from the right according to FIG. 1,
Fig. 3
2 shows a view of the pistons with piston carrier, as seen from FIG. 1 from the left
Fig. 4
an advantageous embodiment of a seal between two moving parts.
Fig. 5
an axial view of a piston carrier with pistons and
Fig. 6
a sectional view of the arrangement of FIG. 5, taken along the line VI-VI.

Gemäß Fig. 1 weist eine Drehkolben-Brennkraftmaschine ein insgesamt mit 2 bezeichnetes Gehäuse auf, das aus einem Motorgehäuse 4 und einem Getriebegehäuse 6 besteht. Das Motorgehäuse besteht aus zwei Schalen 4a, 4b, die zwischen sich einen nach innen offenen kreisringförmigen Zylinderraum 8 einschließen, und deren Schale 4a mit dem Getriebegehäuse 2 verblockt ist. In dem Zylinderraum 8 laufen insgesamt 4, in Fig. 1 nicht dargestellte Kolben um, von denen je zwei sich diametral gegenüberliegend an einem von zwei Kolbenträgern 10 und 12 befestigt ist. Die Kolbenträger sind zum Zylinderraum 8 hin mit derartigen Umfangsflächen versehen, daß sie die Innenfläche des Zylinderraums zu einem kreisförmigen Querschnitt ergänzen, wobei der eine Kolbenträger jeweils eine Lauffläche für die an ihm nicht befestigten Kolben bildet.1, a rotary piston internal combustion engine has a housing, designated overall by 2, which consists of a motor housing 4 and a gear housing 6. The motor housing consists of two shells 4a, 4b, which enclose between them an inwardly open annular cylinder space 8, and whose shell 4a is blocked with the transmission housing 2. A total of 4 pistons, not shown in FIG. 1, circulate in the cylinder chamber 8, two of which are fastened diametrically opposite one another to one of two piston carriers 10 and 12. The piston carriers are provided towards the cylinder chamber 8 with such peripheral surfaces that they complement the inner surface of the cylinder chamber to a circular cross-section, the one piston carrier forming a running surface for the pistons not attached to it.

Der Kolbenträger 12 ist drehfest mit einer Hohlwelle 14 verbunden, die in das Getriebegehäuse 6 einragt und einen radialen Arm 16 aufweist, der über ein Pleuel 18 mit einer Kurbelwelle 20 verbunden ist.The piston carrier 12 is connected in a rotationally fixed manner to a hollow shaft 14 which projects into the gear housing 6 and has a radial arm 16 which is connected to a crankshaft 20 via a connecting rod 18.

Ähnlich ist der Kolbenträger 10 starr an einer Welle 22 befestigt, die sich innerhalb der Hohlwelle 14 in das Getriebegehäuse 6 erstreckt und in einem radialen Arm 24 endet, der über ein Pleuel 26 mit einer Kurbelwelle 28 verbunden ist.Similarly, the piston carrier 10 is rigidly attached to a shaft 22 which extends within the hollow shaft 14 into the gear housing 6 and ends in a radial arm 24 which is connected to a crankshaft 28 via a connecting rod 26.

Die Kurbelwellen 26 und 28 sind in einem Kurbelgehäuse 30 gelagert und enden in drehfest mit ihnen verbundenen Zahnrädern 32, 34, die mit einem Getriebegehäuse-festen Zahnrad 26 kämmen. Das Kurbelgehäuse 30 ist innerhalb des Getriebegehäuses 6 drehbar und reicht mit einer Abtriebswelle 38 durch das Getriebegehäuse hindurch.The crankshafts 26 and 28 are mounted in a crankcase 30 and end in gearwheels 32, 34 connected to them in a rotationally fixed manner, which mesh with a gearwheel 26 fixed to the gearbox housing. The crankcase 30 is rotatable within the gear housing 6 and extends with an output shaft 38 through the gear housing.

Die Zähnezahlen der Zahnräder 32, 34 und 36 sind derart aufeinander abgestimmt, daß sich die Kurbelwellen 20 und 28 während einer Umdrehung des Kurbelgehäuses 30 zweimal drehen, so daß jeder zwischen den Kolben im Zylinderraum 8 ausgebildete Arbeitsraum im Laufe einer vollständigen Umdrehung sich zweimal vergrößert und verkleinert, so daß bei Vorhandensein eines nicht dargestellten Ansaugkanals und eines nicht dargestellten Auslaßkanals ein Viertaktarbeitsverfahren durchführbar ist.The number of teeth of the gears 32, 34 and 36 are matched to one another such that the crankshafts 20 and 28 rotate during one revolution of the crankcase 30 Turn twice so that each working space formed between the pistons in the cylinder space 8 increases and decreases twice in the course of a complete revolution, so that a four-stroke working method can be carried out in the presence of an intake duct and an exhaust duct, not shown.

Fig. 3 zeigt eine Ansicht gemäß Fig. 1 von links mit teilweise aufgeschnittener Schale 4a. Dabei sind die beiden Kolbenträger 10 und 12 sichtbar, wobei der Durchmesser des Kolbenträgers 12 etwas vergrößert dargestellt ist, sowie je einer der auf den Kolbenträgern befestigten Kolben 38 und 40. Der zwischen den Kolben 38 und 40 eingeschlossene Arbeitsraum 42 hat gerade minimale Größe und befindet sich im Bereich einer Zündkerze 44, die vorgesehen ist, wenn die Brennkraftmaschine als Ottomotor arbeitet.FIG. 3 shows a view according to FIG. 1 from the left with the shell 4a partially cut open. The two piston carriers 10 and 12 are visible, the diameter of the piston carrier 12 being shown somewhat enlarged, and one each of the pistons 38 and 40 fastened to the piston carriers. The working space 42 enclosed between the pistons 38 and 40 is just minimal in size and is located in the area of a spark plug 44, which is provided when the internal combustion engine is operating as a gasoline engine.

Fig. 4 zeigt die Ausbildung einer Gleitringdichtung, wie sie an in Fig. 1 mit X bezeichneten Stellen zwischen jeweils zwei beweglichen Bauteilen, das heißt Gehäuseschale und Kolbenträger oder den beiden Kolbenträgern, verwendbar ist. Im dargestellten Beispiel sitzt die Dichtung zwischen der Schale 4a und dem Kolbenträger 10. Die Schale 4a ist mit einer Ringnut 46 versehen, in der ein als Gleitring wirksamer Dichtring 47 angeordnet ist, der unter weitgehender Passung in die Ringnut 46 großflächig am Kolbenträger 10 anliegt. Um den Dichtring 47 drehfest in der Schale 4a zu halten und ihn an den Kolbenträger 10 anzudrücken, sind über den Umfang der Ringnut 46 Sacklöcher 48 verteilt, in denen je eine Feder 50 angeordnet ist, die einen Stift 52 in eine Ausnehmung des Dichtrings 47 drückt. Es versteht sich, daß nicht in jedem der Sacklöcher ein Stift vorhanden sein muß, da die Drehsicherung beispielsweise bereits mit drei in gleichen Winkelabständen verteilten Stiften erzielt wird. Zur gleichmäßigen Anpressung des Dichtrings 47 an den Kolbenträger 10 ist es vorteilhaft, mehrere Federn 50, beispielsweise 18, gleichmäßig über den Umfang der Ringnut 46 zu verteilen.Fig. 4 shows the formation of a mechanical seal, as it can be used at points designated by X in Fig. 1 between two movable components, that is, the housing shell and piston carrier or the two piston carriers. In the example shown, the seal sits between the shell 4a and the piston carrier 10. The shell 4a is provided with an annular groove 46, in which a sealing ring 47, which acts as a sliding ring, is arranged, which over a large area rests against the piston carrier 10 in the annular groove 46. In order to hold the sealing ring 47 in a rotationally fixed manner in the shell 4a and to press it against the piston carrier 10, blind holes 48 are distributed over the circumference of the annular groove 46, in each of which a spring 50 is arranged which presses a pin 52 into a recess in the sealing ring 47 . It goes without saying that a pin does not have to be present in each of the blind holes, since the rotation lock is already achieved, for example, with three pins distributed at equal angular intervals. To evenly press the sealing ring 47 against the piston carrier 10, it is advantageous to distribute a plurality of springs 50, for example 18, evenly over the circumference of the annular groove 46.

Um eine zuverlässige Abdichtung gegenüber Blowbygasen zu erzielen, die in den Spaltraum 56 gelangen, ist der Dichtring 47 mit einer umlaufenden Ringnut 58 versehen, in die zwei als Dichtringe wirksame Federringe 60, 62 derart eingesetzt sind, daß ihre Spalte gegenseitig beispielsweise um 180° verdreht sind. Über geeignete Mittel, beispielsweise Stifte oder Ausbauchungen des Grundes der Ringnut 58 können die Dichtringe 60, 62 drehfest gehalten werden. Die Anordnung der Dichtringe 60, 62 auf der radial äußeren Seite hat den Vorteil, daß von den Wellen 14, 22 bzw. gemäß Fig. 4 von unten kommendes Schmiermittel bis in den Spaltraum zwischen dem Dichtring 47 und der Schale 4a vordringen kann, so daß es die Anlage des Dichtrings 47 am Kolbenträger 10 zusätzlich unterstützt.In order to achieve a reliable seal against blow-by gases which enter the gap space 56, the sealing ring 47 is provided with a circumferential annular groove 58, into which two spring rings 60, 62 which act as sealing rings are inserted such that their gaps are mutually rotated, for example, by 180 °. The sealing rings 60, 62 can be held in a rotationally fixed manner by means of suitable means, for example pins or bulges of the base of the annular groove 58. The arrangement of the sealing rings 60, 62 on the radially outer side has the advantage that lubricant coming from the shafts 14, 22 or according to FIG. 4 can penetrate into the gap between the sealing ring 47 and the shell 4a, so that it additionally supports the installation of the sealing ring 47 on the piston carrier 10.

Mit der beschriebenen Dichtung wird eine außerordentliche sichere Abdichtung erzielt, wobei die großflächige Anlage zwischen Dichtring 47 und Kolbenträger 10 zusätzlich für eine Kühlung des Kolbenträgers sorgt. Es versteht sich, daß zum Andrücken des Dichtrings 47 gegen den Kolbenträger 10 auch Öldruck verwendet werden kann, der der Anordnung gemäß Fig. 4 von links her zugeleitet wird.An extraordinarily secure seal is achieved with the seal described, the large-area contact between the sealing ring 47 and the piston carrier 10 additionally ensuring cooling of the piston carrier. It goes without saying that oil pressure can also be used to press the sealing ring 47 against the piston carrier 10, which oil pressure is supplied to the arrangement according to FIG. 4 from the left.

Gemäß Fig. 5 ist der Kolbenträger 10 über eine Innenverzahnung an der Welle 22 befestigt. Der Kolbenträger 10 umfaßt zwei Speichen 64, von denen nur die obere Speiche mit dem einteilig mit ihr ausgebildeten Kolben 38 dargestellt ist. An der Speiche 64 ist ein Ringteil 66 angebracht, welches zusammen mit dem Kolbenträger 22 umläuft und zusammen mit einem entsprechenden, an dem anderen Kolbenträger befestigten Ringteil 68 den Zylinderraum 8 in Richtung zur Welle 22 hin abschließt.5, the piston carrier 10 is fastened to the shaft 22 via an internal toothing. The piston carrier 10 comprises two spokes 64, of which only the upper spoke with the piston 38 formed in one piece with it is shown. A ring part 66 is attached to the spoke 64, which rotates together with the piston carrier 22 and, together with a corresponding ring part 68 fastened to the other piston carrier, closes off the cylinder space 8 in the direction of the shaft 22.

Wie aus Fig. 6 ersichtlich, ist der Kolben 38 im nicht betriebswarmen Zustand des Motors exzentrisch zum Zylinderraum 8 angeordnet, so daß er sich bei Erwärmung in Folge der Ausdehnung seines Materials und des Materials der Speiche 64 in eine zentrische Lage bewegt. Die Abdichtung zwischen dem Kolben 38 und der Innenwand des Zylinderraums 8 wird von Kolbenringen 70 übernommen.As can be seen from FIG. 6, the piston 38 is arranged eccentrically to the cylinder space 8 when the engine is not in the operating state, so that it moves into a central position when heated due to the expansion of its material and the material of the spoke 64. The seal between the piston 38 and the inner wall of the cylinder space 8 is taken over by piston rings 70.

Vorteilhaft ist, wenn die Kolbenträger 10, 12 aus einem Material mit einem geringeren thermischen Ausdehnungskoeffizienten als das Material des Motorgehäuses 4 bestehen, da das Motorgehäuse 4 unmittelbar wassergekühlt sein kann, wohingegen die Kolbenträger einer Wasserkühlung nur schwer zugänglich sind.It is advantageous if the piston carrier 10, 12 consist of a material with a lower coefficient of thermal expansion than the material of the motor housing 4, since the motor housing 4 can be directly water-cooled, whereas the piston carrier are difficult to access for water cooling.

Die dargestellte Ausführungsform des Kolbenträgers 10 mit den Speichen 64 und dem Ringteil 66 hat folgenden Vorteil:The illustrated embodiment of the piston carrier 10 with the spokes 64 and the ring part 66 has the following advantage:

Auf den Kolben 38 wirken bei dessen Umlauf erhebliche Zentrifugalkräfte. Außerdem wird vom Kolben 38 über die Speichen 64 das gesamte Drehmoment auf die Welle 22 übertragen, so daß die Speichen aus hochfestem Material bestehen sollten. Ein solches hochfestes Material hat im allgemeinen schlechte Gleiteigenschaften, die jedoch für die Wand des Zylinderraums 8 maßgeblich sind. Deshalb sind die Ringteile 66 und 68 aus einem Material mit guten Gleiteigenschaften, beispielsweise Grauguß oder beschichtetem Aluminium hergestellt. Vorteilhaft ist außerdem, wenn der zwischen dem Ringteil 66, 68 und der zugehörigen Schale 4b, 4a des Motorgehäuses ausgebildete Spalt, wie in Fig. 6 dargestellt, senkrecht in den Zylinderraum 8 einläuft. Dadurch entstehen keine scharfen Grate, können die Kolbenringe 70 zuverlässig abdichten und können die Spalte näher zum Zylinderraum 8 abgedichtet werden, wodurch die Leckverluste vermindert werden.Considerable centrifugal forces act on the piston 38 as it rotates. In addition, the entire torque is transmitted from the piston 38 to the shaft 22 via the spokes 64, so that the spokes should be made of high-strength material. Such a high-strength material generally has poor sliding properties, but these are decisive for the wall of the cylinder space 8. The ring parts 66 and 68 are therefore made of a material with good sliding properties, for example gray cast iron or coated aluminum. It is also advantageous if the gap formed between the ring part 66, 68 and the associated shell 4b, 4a of the motor housing, as shown in FIG. 6, runs vertically into the cylinder space 8. As a result, there are no sharp burrs, the piston rings 70 can reliably seal and the gaps can be sealed closer to the cylinder space 8, as a result of which the leakage losses are reduced.

Claims (8)

Drehkolben-Brennkraftmaschine, mit einem Gehäuse (4), das einen kreisringförmigen Zylinderraum (8) enthält, einer geraden Anzahl von in dem Zylinderraum umlaufenden Kolben (38,40) mit dem Zylinderraum angepaßten kreisförmigen Querschnitt, zwei um die Ringachse des Zylinderraums drehbar gelagerten Kolbenträgern (10,12), an denen jeweils die halbe Anzahl von Kolben befestigt sind,    wobei die Umfangsflächen der Kolbenträger (10,12) derart ausgebildet sind, daß sie die Innenfläche des Zylinderraums zu einem den Kolben (38,40) entsprechenden kreisförmigen Querschnitt ergänzen, gegen den an den Kolben vorgesehene Kolbenringe (70) abdichten, und
   mit jeweils mindestens einem zwischen den Kolbenträgern (10,12) und zwischen jedem Kolbenträger und einer gegenüberliegenden Wand des Gehäuses in einer Ringnut (46) des Gehäuses bzw. eines Kolbenträgers aufgenommenen Dichtring (47),
   dadurch gekennzeichnet, daß
   der in der Ringnut (46) des Gehäuses (4) bzw. eines der Kolbenträger (10,12) aufgenommene Dichtring (47) mit einer aus der Ringnut heraus wirkenden Kraft beaufschlagt an einer Gegenfläche des jeweiligen Kolbenträgers anliegt.Rotary piston internal combustion engine, with a housing (4) which contains an annular cylinder space (8), an even number of pistons (38, 40) rotating in the cylinder space and having a circular cross section matched to the cylinder space, two piston supports (10, 12) rotatably mounted about the ring axis of the cylinder space, to which half the number of pistons are attached, wherein the peripheral surfaces of the piston carrier (10, 12) are designed such that they complement the inner surface of the cylinder space to form a circular cross section corresponding to the piston (38, 40), against which piston rings (70) provided on the piston seal, and
each with at least one sealing ring (47) received between the piston carriers (10, 12) and between each piston carrier and an opposite wall of the housing in an annular groove (46) of the housing or a piston carrier,
characterized in that
the sealing ring (47) received in the annular groove (46) of the housing (4) or one of the piston carriers (10, 12) is acted upon by a force acting out of the annular groove and bears against a counter surface of the respective piston carrier. Drehkolben-Brennkraftmaschine nach Anspruch 1,
   dadurch gekennzeichnet,
   daß zwischen dem Boden der Ringnut (46) und dem Dichtring (47) eine Feder (50) angeordnet ist.Rotary piston internal combustion engine according to claim 1,
characterized by
that between the bottom of the annular groove (46) and the sealing ring (47) a spring (50) is arranged. Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 oder 2
   dadurch gekennzeichnet,
   daß zwischen einem Sackloch (48) im Boden der Ringnut (46) und einer Ausnehmung des Dichtrings (47) ein Stift (52) angeordnet ist, der den Dichtring gegen Verdrehen sichert.Rotary piston internal combustion engine according to one of claims 1 or 2
characterized by
that a pin (52) is arranged between a blind hole (48) in the bottom of the annular groove (46) and a recess of the sealing ring (47), which secures the sealing ring against rotation. Drehkolben-Brennkraftmaschine nach Anspruch 2 oder 3,
   dadurch gekennzeichnet,
   daß der Dichtring (47) an seiner innerhalb der Ringnut liegenden, radial äußeren Fläche mit einer umlaufenden Nut (58) versehen ist, in der wenigstens ein gegen die Ringnut dichtender, Federring (60) angeordnet ist.Rotary piston internal combustion engine according to claim 2 or 3,
characterized by
that the sealing ring (47) is provided on its inside the ring groove, the radially outer surface with a circumferential groove (58), in which at least one spring ring (60) sealing against the ring groove is arranged. Drehkolben-Brennkraftmaschine nach Anspruch 4,
   dadurch gekennzeichnet,
   daß in der Ringnut (58) zwei mit ihren Spalten gegeneinander versetzte Federringe (60,62) angeordnet sind.Rotary piston internal combustion engine according to claim 4,
characterized by
that in the annular groove (58) two spring rings (60, 62) offset with their gaps are arranged. Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 bis 5,
   dadurch gekennzeichnet, daß
   der zwischen jedem Kolbenträger (10,12) und der benachbarten Gehäusefläche ausgebildete Spalt etwa rechtwinklig in den Zylinderraum (8) mündet.Rotary piston internal combustion engine according to one of claims 1 to 5,
characterized in that
the gap formed between each piston carrier (10, 12) and the adjacent housing surface opens approximately at right angles into the cylinder space (8). Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 bis 6,
   dadurch gekennzeichnet,
   daß die Kolbenträger (10,12) aus einem Material mit geringerer Wärmedehnung als das Material des Gehäuses (4) bestehen.Rotary piston internal combustion engine according to one of claims 1 to 6,
characterized by
that the piston carrier (10, 12) consist of a material with less thermal expansion than the material of the housing (4). Drehkolben-Brennkraftmaschine nach einem der Ansprüche 1 bis 7,
   dadurch gekennzeichnet,
   daß der Kolbenträger mit seiner Nabe verbundene Speichen (64) aus einem Material hoher Festigkeit und einen die Innenfläche des Zylinderraums (8) ergänzenden Ringteil (66) mit einer Lauffläche aus einem Material mit guten Gleiteigenschaften aufweist.Rotary piston internal combustion engine according to one of claims 1 to 7,
characterized by
that the piston carrier with its hub has spokes (64) made of a high-strength material and an annular part (66) supplementing the inner surface of the cylinder space (8) with a tread made of a material with good sliding properties.
EP96110913A 1995-07-27 1996-07-05 Rotary internal combustion engine Withdrawn EP0756068A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19527396 1995-07-27
DE19527396A DE19527396C2 (en) 1995-07-27 1995-07-27 Rotary piston internal combustion engine

Publications (2)

Publication Number Publication Date
EP0756068A2 true EP0756068A2 (en) 1997-01-29
EP0756068A3 EP0756068A3 (en) 1998-01-28

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US5996538A (en) * 1998-06-03 1999-12-07 Rocha; Octavio Two-cycle internal combustion engine and method of operation
US6289867B1 (en) * 1999-03-31 2001-09-18 Cummins Engine Company, Inc. Rotary engine
NZ513155A (en) * 2001-07-25 2004-02-27 Shuttleworth Axial Motor Compa Improvements relating to axial motors
RU2343290C2 (en) * 2003-09-15 2009-01-10 Вячеслав Иванович Коваленко Rotor-type internal combustion engine
US6895922B1 (en) 2004-08-09 2005-05-24 Gloria Snowden-Wood Rotary opposed piston engine
US7600490B2 (en) * 2006-05-30 2009-10-13 Reisser Heinz-Gustav A Internal combustion engine
US7730869B2 (en) * 2007-04-13 2010-06-08 Yan Li Housing wheel engine
EP2643553B1 (en) 2010-11-25 2017-03-29 AVL List GmbH Rotary piston machine, especially rotary engine

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US1994858A (en) * 1932-07-29 1935-03-19 Stromberg Seal for rotary engines and the like
DE1450405A1 (en) * 1964-03-26 1969-03-06 Sabet Dipl Ing Huschang Annular sealing element, especially for rotary piston internal combustion engines
US3854457A (en) * 1971-10-11 1974-12-17 Taurozzi A Rotary engine
US3890939A (en) * 1973-03-22 1975-06-24 Alex A Mcintosh Rotary engine with improved seal and timing mechanism providing linear acceleration between pistons during the power stroke
US4072447A (en) * 1973-07-02 1978-02-07 Peter Gaspar Alternating piston rotary apparatus
US4243233A (en) * 1978-06-12 1981-01-06 Yoshio Arai Seal ring having a tapered surface, and a sealing device

Also Published As

Publication number Publication date
US5740765A (en) 1998-04-21
DE19527396C2 (en) 1998-11-12
DE19527396A1 (en) 1997-02-06
EP0756068A3 (en) 1998-01-28

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