EP0337950A2 - Internal axis rotary piston engine - Google Patents

Internal axis rotary piston engine Download PDF

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Publication number
EP0337950A2
EP0337950A2 EP89810265A EP89810265A EP0337950A2 EP 0337950 A2 EP0337950 A2 EP 0337950A2 EP 89810265 A EP89810265 A EP 89810265A EP 89810265 A EP89810265 A EP 89810265A EP 0337950 A2 EP0337950 A2 EP 0337950A2
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EP
European Patent Office
Prior art keywords
rotor disk
axially
rotary piston
shaft
rotors
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Granted
Application number
EP89810265A
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German (de)
French (fr)
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EP0337950B1 (en
EP0337950A3 (en
Inventor
Felix Dr.H.C. Wankel
Frank Obrist
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Meysen Fried
Renz Gerhard
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Meysen Fried
Renz Gerhard
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Priority to AT89810265T priority Critical patent/ATE78080T1/en
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Publication of EP0337950A3 publication Critical patent/EP0337950A3/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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to an inner-axis rotary lobe machine with at least two inner rotors fastened to a common shaft and a corresponding number of outer rotors, which are enclosed by a common housing and are arranged axially next to one another, the engagement parts of the outer rotors in the circumferential direction with one another and in the axial direction with those of the adjacent one Outer rotor are rigidly connected by an annular, axially inner rotor disk, so that it surrounds the shaft of the inner rotor and axially divides the working spaces of the machine.
  • Machines of this type are known, for example, from FIGS. 22 and 27 of US Pat. No. 3,954,355. These machines are designed in such a way that their inner runners always laterally cover the space enclosed by the axially inner rotor disk, so that the axially adjacent working spaces are sealed off from one another. According to FIG. 27 of this US Pat. No. 3,954,355, the gear drive connection between an inner rotor pair and an outer rotor pair is arranged in this space enclosed by the rotor disk.
  • the invention has for its object to find a machine of the type mentioned that the stiffening connection between a plurality of external rotors, or. the axial subdivision of an outer rotor is also made possible for machines whose working spaces extend radially inward beyond the possible radially inner boundary of an outer rotor disk, so that the machine has an increased throughput volume.
  • the aforementioned radially inner boundary of an outer rotor disk is structurally due to the necessary radially offset arrangement of the shaft of the inner rotor relative to the axis of rotation of the outer rotor.
  • this object is achieved in that the space enclosed by the axially inner rotor disk is filled by a partition wall body, a bearing being provided between the rotor disk and the partition wall body and between this and the shaft, and working spaces of the machine up to the partition wall body reach up.
  • the partition body is not connected to any stationary part, and although it is only connected to rotating parts, i.e. In the radial direction, on the one hand, it borders on the rotor disk surrounding it and, on the other hand, on the shaft it encloses, it stands still itself. This results from the radial displacement of the axes of the two bearings mentioned.
  • the inner rotors 2, 3 and the outer rotors 4, 5 of the rotary piston machine shown rotate about axes 7, 8 which are fixed relative to the common machine housing 6, so that very high rotational speeds are possible.
  • the three engagement parts 4a, 4b, 4c of the outer rotor 4 could easily be produced from rod material with a relatively large axial length due to their constant cross-section in the axial direction. Due to bending loads caused by centrifugal forces, the free axial length of the engagement parts 4a, 4b, 4c is limited by an axially inner rotor disk 9, which rigidly connects these engagement parts 4a, 4b, 4c to one another in the circumferential direction.
  • the rigid connection is provided, for example, by a one-piece production of the engagement parts 4a, 4b, 4c with the rotor disk 9.
  • the axially adjacent outer and inner rotors 2 to 5 are preferably offset from one another in the circumferential direction by 180 °. The load peaks resulting from the compression in the machine consequently occur on both axially adjacent rotors 2, 3 and 4.5 not at the same time.
  • the size of the inner diameter of the axially inner rotor disk 9 is in the range due to the eccentricity of the shaft axis 7 of the inner rotor 2, 3, which is best seen in FIG of the rotor disk 9, wherein the required arrangement of a bearing 13 on the inner diameter 14 must also be taken into account, which keeps the frictional resistance between a partition wall body 15 enclosed by the rotor disk 9 and stationary relative to the machine housing 6 low.
  • This bearing 13 is therefore preferably designed as a roller bearing. In the illustrated embodiment, this bearing 13 is enclosed in circumferential grooves of the rotor disk 9 and the partition wall body 15, so that it is sealed against the working spaces 16 of the machine. It goes without saying that the bearing 13 or.
  • the roller bearing can also be provided in only one circumferential groove of the rotor disk 9 or the partition wall body 15.
  • the axial sealing of the annular gap between the rotor disk 9 and the partition wall body can be carried out by its narrow dimensions or by sealing rings 17, 18 engaging in a groove.
  • the working spaces 16 of a rotary piston machine extend radially inward substantially beyond the inner diameter 14 of the axially inner rotor disk 9 and become therein Extent area 19 limited in the axial direction by the partition wall body 15, which extends in the same plane as the rotor disk 9 and thus forms the radially inner continuation of the side surfaces 9a, 9b delimiting the working spaces 16.
  • the combination of the axially inner rotor disk 9 with the thus also axially inner partition wall body 15 results in an axial one Subdivision of the working spaces 16 of the machine, so that an axially separated area of the machine can be arranged as a high-pressure stage behind a first low-pressure stage.
  • FIG. 3 shows the flow channels 20, 21 between a low-pressure part 22 and a high-pressure part 23 of a rotary piston machine according to the invention, which are guided via an intercooler 24 around the gas heated by the compression in the low-pressure part 22 before it is further compressed in the high-pressure part 23 cool down.
  • the coolant circulates through the pipes 25, 26.
  • the outer rotor unit formed from the two outer rotors 4, 5 carries annular end bodies 30, 31 which are connected to the engaging parts 4a, 4b, 4c; 5a, 5b, 5c are screwed on, as indicated by lines 32, 33.
  • the outer rotor unit 4.5 is supported by means of roller bearings 34, 35, which are supported on filler bodies 38, 39 that are firmly connected to housing side plates 36, 37.
  • the gear-gear connection 10, 11 between the outer and inner rotor units 4, 5; 2, 3 in the speed ratio of 2: 3 is arranged between an outer and inner filler body 38, 40, which are screwed together.
  • the shaft 12 of the inner rotor unit 2, 3 is mounted in roller bearings 41, 42 which are held in the filler bodies 38, 39.
  • the bearing 43 between the axially inner partition wall body 15 and the shaft 12 is less stressed, since the bearing forces occurring there merely cause the separation to rotate to prevent wall body 15 with the axially inner rotor 9.
  • This bearing can accordingly be formed by a thin bearing shell 43.
  • the machine's inlet and outlet ports 44, 45 are located on the circumference of the housing 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
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  • Hydraulic Motors (AREA)
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Abstract

The rotary piston machine has two internal rotors (2, 3) fixed to a common shaft (12) and two external rotors (4, 5) rigidly interconnected by means of an annular rotor disk (9). The working spaces (16) between the engagement parts of both external rotors (4, 5) extend a maximum extension (19) radially inward past the inner boundary of rotor disk (9). For the axial sealing of the working spaces (16), also in the area of said extension (19), the rotor disk (9) encloses a partition body (15), which surrounds the shaft (12) of the internal rotors (2, 3) by means of a bearing (43). A further bearing (13) is provided between rotor disk (9) and partition body (15). Partition body (15) is prevented from concomitant rotation with one of the two rotary machine parts (9, 12) adjacent thereto as a result of the radial displacement of the shaft (12) engaging therein relative to the rotation axis of rotor disk (9). Partition body (15) permits the axial subdivision of the machine into a low pressure part (22) and a high pressure part (23), accompanied by a reinforcement of the engagement parts of the external rotor (4, 5) by its rigid connection to the rotor disk (9).

Description

Die Erfindung betrifft eine innenachsige Drehkolbenmaschine mit mindestens zwei auf einer gemeinsamen Welle befestigten Innenläufern und einer entsprechenden Anzahl von Aussenläu­fern, die von einem gemeinsamen Gehäuse umschlossen und axial nebeneinander angeordnet sind, wobei die Eingriffs­teile der Aussenläufer in Umfangsrichtung miteinander und in axialer Richtung mit denjenigen des benachbarten Aussen­läufers durch eine kreisringförmige, axial innere Läufer­scheibe starr verbunden sind, so dass diese die Welle der Innenläufer umschliesst und die Arbeitsräume der Maschine axial unterteilt.The invention relates to an inner-axis rotary lobe machine with at least two inner rotors fastened to a common shaft and a corresponding number of outer rotors, which are enclosed by a common housing and are arranged axially next to one another, the engagement parts of the outer rotors in the circumferential direction with one another and in the axial direction with those of the adjacent one Outer rotor are rigidly connected by an annular, axially inner rotor disk, so that it surrounds the shaft of the inner rotor and axially divides the working spaces of the machine.

Maschinen dieser Art sind beispielsweise durch die Fig.22 und 27 der US-PS 3,954,355 bekannt. Diese Maschinen sind so ausgeführt, dass ihre Innenläufer stets den von der axial inneren Läuferscheibe umschlossenen Raum seitlich über­decken, so dass die axial benachbarten Arbeitsräume gegen einander abgedichtet sind. Gemäss Fig. 27 dieser US-PS 3,954,355 ist in diesem von der Läuferscheibe umschlossenen Raum die Zahnrad-Antriebsverbindung zwischen einem Innen­läuferpaar und einem Aussenläuferpaar angeordnet. Dort je­doch, wo zwischen zwei axial benachbarten Aussenläufern eine radiale Abstützung erfolgen soll, ist eine starr mit dem Maschinengehäuse verbundene,axial innere Trennwand vor­handen, in der die Welle der Innenläufer gelagert ist und die über einen an ihr angeformten zylindrischen Innenkör­per zwei kreisringförmige, axial innere Aussenläuferscheiben radial lagert. Eine solche Trennwand verhindert jedoch die direkte axiale Verbindung zwischen zwei Aussenläufern über eine kreisringförmige Läuferscheibe und führt zu einer auf­wendigeren Gehäusekonstruktion.Machines of this type are known, for example, from FIGS. 22 and 27 of US Pat. No. 3,954,355. These machines are designed in such a way that their inner runners always laterally cover the space enclosed by the axially inner rotor disk, so that the axially adjacent working spaces are sealed off from one another. According to FIG. 27 of this US Pat. No. 3,954,355, the gear drive connection between an inner rotor pair and an outer rotor pair is arranged in this space enclosed by the rotor disk. However, where radial support is to take place between two axially adjacent outer rotors, there is an axially inner partition wall rigidly connected to the machine housing, in which the shaft of the inner rotor is mounted and which has two circular, axially inner ones via a cylindrical inner body molded onto it Outer rotor discs are supported radially. Such a partition wall, however, prevents the direct axial connection between two external rotors via an annular rotor disk and leads to a more complex housing construction.

Der Erfindung liegt die Aufgabe zugrunde, eine Maschine der eingangs genannten Art zu finden, die bei einfacher Gehäuse­gestaltung die versteifende Verbindung zwischen mehreren Aussenläufern,bzw. die axiale Unterteilung eines Aussen­läufers,auch für Maschinen ermöglicht, deren Arbeitsräume sich radial nach innen über die mögliche radial innere Be­grenzung einer Aussenläuferscheibe erstrecken, so dass die Maschine ein vergrössertes Durchsatzvolumen hat. Die ge­nannte radial innere Begrenzung einer Aussenläuferscheibe ist durch die notwendige radial versetzte Anordnung der Welle der Innenläufer relativ zur Drehachse der Aussenläufer konstruktiv bedingt.The invention has for its object to find a machine of the type mentioned that the stiffening connection between a plurality of external rotors, or. the axial subdivision of an outer rotor is also made possible for machines whose working spaces extend radially inward beyond the possible radially inner boundary of an outer rotor disk, so that the machine has an increased throughput volume. The aforementioned radially inner boundary of an outer rotor disk is structurally due to the necessary radially offset arrangement of the shaft of the inner rotor relative to the axis of rotation of the outer rotor.

Die Lösung der genannten Aufgabe erfolgt erfindungsgemäss dadurch, dass der von der axial inneren Läuferscheibe um­schlossene Raum durch einen Trennwandkörper ausgefüllt ist, wobei zwischen der Läuferscheibe und dem Trennwandkörper sowie zwischen diesem und der Welle jeweils eine Lagerung vorgesehen ist und Arbeitsräume der Maschine bis an den Trennwandkörper heranreichen.According to the invention, this object is achieved in that the space enclosed by the axially inner rotor disk is filled by a partition wall body, a bearing being provided between the rotor disk and the partition wall body and between this and the shaft, and working spaces of the machine up to the partition wall body reach up.

Aufgrund der genannten Definition der Erfindung ergibt sich, dass der Trennwandkörper mit keinem stillstehenden Teil ver­bunden ist, und obwohl er nur an sich drehende Teile, d.h. in radialer Richtung einerseits an die ihn umschliessende Läuferscheibe und andererseits an die von ihm umschlossene Welle, angrenzt, steht er selbst still. Dies ergibt sich durch die radiale Versetzung der Achsen der beiden genannten Lagerungen.Based on the above definition of the invention, it follows that the partition body is not connected to any stationary part, and although it is only connected to rotating parts, i.e. In the radial direction, on the one hand, it borders on the rotor disk surrounding it and, on the other hand, on the shaft it encloses, it stands still itself. This results from the radial displacement of the axes of the two bearings mentioned.

Zum besseren Verständnis der Erfindung wird auf die folgende Beschreibung eines in den Zeichnungen dargestellten Ausfüh­rungsbeispieles hingewiesen. Es zeigt:

  • Fig.1 einen Axialschnitt durch eine erfindungsgemässe innenachsige Drehkolbenmaschine,
  • Fig.2 einen Radialschnitt durch die Drehkolbenmaschine nach Fig.1, entlang der Linie II-II und
  • Fig.3 eine Aufsicht auf eine zweistufig arbeitende erfindungsgemässe Rotationskolbenmaschine.
For a better understanding of the invention, reference is made to the following description of an embodiment shown in the drawings. It shows:
  • 1 shows an axial section through an inner-axis rotary piston machine according to the invention,
  • 2 shows a radial section through the rotary piston machine according to Figure 1, along the line II-II and
  • 3 shows a plan view of a two-stage rotary piston machine according to the invention.

Gemäss dem Prinzip von Drehkolbenmaschinen drehen sich die Innenläufer 2,3 und die Aussenläufer 4,5 der dargestellten Rotationskolbenmaschine um relativ zum gemeinsamen Maschi­nengehäuse 6 feststehend angeordnete Achsen 7,8, so dass sehr hohe Drehgeschwindigkeiten möglich sind. Die drei Ein­griffsteile 4a,4b,4c des Aussenläufers 4 liessen sich auf­grund ihres in Axialrichtung konstanten Querschnittes aus Stangmaterial leicht mit verhältnismässig grosser axialer Länge herstellen. Aufgrund von Biegebelastungen durch Zentri­fugalkräfte ist die freie axiale Länge der Eingriffsteile 4a,4b,4c durch eine axial innere Läuferscheibe 9 begrenzt, die diese Eingriffsteile 4a,4b,4c in Umfangsrichtung starr miteinander verbindet. Die starre Verbindung ist beispiels­weise durch eine einstückige Herstellung der Eingriffsteile 4a,4b,4c mit der Läuferscheibe 9 gegeben.According to the principle of rotary piston machines, the inner rotors 2, 3 and the outer rotors 4, 5 of the rotary piston machine shown rotate about axes 7, 8 which are fixed relative to the common machine housing 6, so that very high rotational speeds are possible. The three engagement parts 4a, 4b, 4c of the outer rotor 4 could easily be produced from rod material with a relatively large axial length due to their constant cross-section in the axial direction. Due to bending loads caused by centrifugal forces, the free axial length of the engagement parts 4a, 4b, 4c is limited by an axially inner rotor disk 9, which rigidly connects these engagement parts 4a, 4b, 4c to one another in the circumferential direction. The rigid connection is provided, for example, by a one-piece production of the engagement parts 4a, 4b, 4c with the rotor disk 9.

Die sich in axialer Richtung jenseits der Läuferscheibe 9 an die Eingriffsteile 4a,4b,4c des einen Aussenläufers 4 anschliessenden Eingriffsteile 5a,5b,5c eines somit vorhan­denen zweiten Aussenläufers 5, von denen in den Zeichnungen Fig.1) nur einer sichtbar ist, können sich gleichachsig an diese anschliessen, so dass die Läuferscheibe 9 lediglich eine Unterbrechung des Axialverlaufs der Eingriffsteile dar­stellt. Für eine gleichmässigere Arbeitsweise der Maschine und damit eine geringere Belastung der Antriebsverbindung zwischen Aussen- und Innenläufern, d.h. der Zahnräder 10,11, sind jedoch die axial aneinandergrenzenden Aussen- und Innenläufer 2 bis 5 vorzugsweise in Umfangsrichtung um 180° versetzt zueinander angeordnet. Die sich durch die Kompres­sion in der Maschine ergebenden Belastungsspitzen treten folglich an beiden axial aneinandergrenzenden Läufern 2,3 und 4,5 nicht gleichzeitig auf.The engagement parts 5a, 5b, 5c of an external runner 5, which is present in the axial direction, beyond the rotor disk 9, on the engagement parts 4a, 4b, 4c of an outer rotor 4, of which there is a second outer rotor 5, of which only one is visible in the drawings FIG. 1) connect to them at the same axis, so that the rotor disk 9 merely represents an interruption in the axial course of the engagement parts. For a more uniform operation of the machine and thus a lower load on the drive connection between the outer and inner rotors, ie the gears 10, 11, however, the axially adjacent outer and inner rotors 2 to 5 are preferably offset from one another in the circumferential direction by 180 °. The load peaks resulting from the compression in the machine consequently occur on both axially adjacent rotors 2, 3 and 4.5 not at the same time.

Die Grösse des inneren Durchmessers der axial inneren Läu­ferscheibe 9 ist durch die am besten in Fig.2 sichtbare Exzentrizität der Wellenachse 7 der Innenläufer 2,3 relativ zur Drehachse 8 der Aussenläufer 4,5 sowie den Aussendurch­messer Welle 12 der Innenläufer 2,3 im Bereich der Läufer­scheibe 9 bestimmt, wobei ausserdem die erforderliche An­ordnung einer Lagerung 13 am Innendurchmesser 14 zu berück­sichtigen ist, die den Reibungswiderstand zwischen einem von der Läuferscheibe 9 umschlossenen, relativ zum Maschi­nengehäuse 6 stillstehenden Trennwandkörper 15 gering hält. Diese Lagerung 13 ist deshalb vorzugsweise als Wälzlager ausgeführt. Beim dargestellten Ausführungsbeispiel ist diese Lagerung 13 in Umfangsnuten der Läuferscheibe 9 und des Trennwandkörpers 15 eingeschlossen, so dass sie gegen die Arbeitsräume 16 der Maschine abgedichtet ist. Es ver­steht sich, dass die Lagerung 13,bzw. das Wälzlager,auch in nur einer Umfangsnut der Läuferscheibe 9 oder des Trenn­wandkörpers 15 vorgesehen sein kann. Die axiale Abdichtung des Ringspaltes zwischen der Läuferscheibe 9 und dem Trenn­wandkörper kann durch dessen enge Bemessung oder durch in eine Nut eingreifende Dichtringe 17,18 erfolgen.The size of the inner diameter of the axially inner rotor disk 9 is in the range due to the eccentricity of the shaft axis 7 of the inner rotor 2, 3, which is best seen in FIG of the rotor disk 9, wherein the required arrangement of a bearing 13 on the inner diameter 14 must also be taken into account, which keeps the frictional resistance between a partition wall body 15 enclosed by the rotor disk 9 and stationary relative to the machine housing 6 low. This bearing 13 is therefore preferably designed as a roller bearing. In the illustrated embodiment, this bearing 13 is enclosed in circumferential grooves of the rotor disk 9 and the partition wall body 15, so that it is sealed against the working spaces 16 of the machine. It goes without saying that the bearing 13 or. the roller bearing can also be provided in only one circumferential groove of the rotor disk 9 or the partition wall body 15. The axial sealing of the annular gap between the rotor disk 9 and the partition wall body can be carried out by its narrow dimensions or by sealing rings 17, 18 engaging in a groove.

Wie in Fig.1 durch den Bereich 19 angedeutet ist und sich auch durch die Darstellung der Fig.2 zeigt, erstrecken sich die Arbeitsräume 16 einer erfindungsgemässen Rotationkol­benmaschine radial nach innen wesentlich über den inneren Durchmesser 14 der axial inneren Läuferscheibe 9 hinaus und werden in diesem Erstreckungsbereich 19 in axialer Richtung durch den Trennwandkörper 15 begrenzt, der sich in gleicher Ebene wie die Läuferscheibe 9 erstreckt und somit die ra­dial innere Fortsetzung von deren die Arbeitsräume 16 be­grenzenden Seitenflächen 9a,9b bildet. Durch die Kombination der axial inneren Läuferscheibe 9 mit dem somit ebenfalls axial inneren Trennwandkörper 15 ergibt sich eine axiale Unterteilung der Arbeitsräume 16 der Maschine, so dass ein somit axial abgetrennter Bereich der Maschine arbeitsmässig als Hochdruckstufe hinter einer ersten Niederdruckstufe angeordnet sein kann. Die Darstellung in Fig.3 zeigt die Strömungskanäle 20,21 zwischen einem Niederdruckteil 22 und einem Hochdruckteil 23 einer erfindungsgemässen Rota­tionskolbenmaschine, die über einen Zwischenkühler 24 ge­führt sind, um das durch die Kompression in dem Niederdruck­teil 22 erwärmte Gas vor seiner weiteren Kompression in dem Hochdruckteil 23 abzukühlen. Das Kühlmittel zirkuliert über die Rohrleitungen 25,26.As indicated in FIG. 1 by the area 19 and also shown by the illustration in FIG. 2, the working spaces 16 of a rotary piston machine according to the invention extend radially inward substantially beyond the inner diameter 14 of the axially inner rotor disk 9 and become therein Extent area 19 limited in the axial direction by the partition wall body 15, which extends in the same plane as the rotor disk 9 and thus forms the radially inner continuation of the side surfaces 9a, 9b delimiting the working spaces 16. The combination of the axially inner rotor disk 9 with the thus also axially inner partition wall body 15 results in an axial one Subdivision of the working spaces 16 of the machine, so that an axially separated area of the machine can be arranged as a high-pressure stage behind a first low-pressure stage. The illustration in FIG. 3 shows the flow channels 20, 21 between a low-pressure part 22 and a high-pressure part 23 of a rotary piston machine according to the invention, which are guided via an intercooler 24 around the gas heated by the compression in the low-pressure part 22 before it is further compressed in the high-pressure part 23 cool down. The coolant circulates through the pipes 25, 26.

Die grundsätzliche Wirkungsweise des dargestellten Ausfüh­rungsbeipieles, insbesondere die Form der sich dynamisch durch die Relativbewegung zwischen Aussen- und Innenläufern verändernden Arbeitsräume 16 zwischen den Eingriffsteilen 4a,4b,4c ist in der DE-PS 34 32 915 näher beschrieben und dargestellt.The basic mode of operation of the exemplary embodiment shown, in particular the shape of the working spaces 16 between the engaging parts 4a, 4b, 4c, which changes dynamically due to the relative movement between outer and inner runners, is described and illustrated in more detail in DE-PS 34 32 915.

An ihren beiden äusseren Enden trägt die aus den beiden Aussenläufern 4,5 gebildete Aussenläufereinheit ringförmige Endkörper 30,31, die an die Eingriffsteile 4a,4b,4c; 5a,5b, 5c angeschraubt sind, wie durch die Linien 32,33 angedeutet ist. Ueber diese Endkörper 32,33 erfolgt die Lagerung der Aussenläufereinheit 4,5 mittels Wälzlagern 34,35, die sich auf mit Gehäuseseitenplatten 36,37 fest verbundenen Aus­füllkörpern 38,39 abstützen. Die Zahnrad-Getriebeverbindung 10,11 zwischen der Aussen- und Innenläufereinheit 4,5;2,3 im Drehzahlverhältnis von 2:3 ist zwischen einem äusseren und inneren Ausfüllkörper 38,40 angeordnet, die fest mit­einander verschraubt sind. Die Welle 12 der Innenläuferein­heit 2,3 ist in Wälzlagern 41,42 gelagert, die in den Aus­füllkörpern 38,39 gehalten sind.At its two outer ends, the outer rotor unit formed from the two outer rotors 4, 5 carries annular end bodies 30, 31 which are connected to the engaging parts 4a, 4b, 4c; 5a, 5b, 5c are screwed on, as indicated by lines 32, 33. Via these end bodies 32, 33, the outer rotor unit 4.5 is supported by means of roller bearings 34, 35, which are supported on filler bodies 38, 39 that are firmly connected to housing side plates 36, 37. The gear-gear connection 10, 11 between the outer and inner rotor units 4, 5; 2, 3 in the speed ratio of 2: 3 is arranged between an outer and inner filler body 38, 40, which are screwed together. The shaft 12 of the inner rotor unit 2, 3 is mounted in roller bearings 41, 42 which are held in the filler bodies 38, 39.

Die Lagerung 43 zwischen dem axial inneren Trennwandkörper 15 und der Welle 12 ist geringer beansprucht, da die dort auftretenden Lagerkräfte lediglich das Mitdrehen des Trenn­ wandkörpers 15 mit der axial inneren Läuferscheibe 9 zu ver­hindern haben. Entsprechend kann diese Lagerung durch eine dünne Lagerschale 43 gebildet sein.The bearing 43 between the axially inner partition wall body 15 and the shaft 12 is less stressed, since the bearing forces occurring there merely cause the separation to rotate to prevent wall body 15 with the axially inner rotor 9. This bearing can accordingly be formed by a thin bearing shell 43.

Die Ein- und Auslassstutzen 44,45 der Maschine befinden sich am Umfang des Gehäuses 6.The machine's inlet and outlet ports 44, 45 are located on the circumference of the housing 6.

Claims (5)

1. Innenachsige Rotationskolbenmaschine mit mindestens zwei auf einer gemeinsamen Welle (12) befestigten Innen­läufern (2,3) und einer entsprechenden Anzahl von Aussen­läufern (4,5) , die von einem gemeinsamen Gehäuse (6) um­schlossen und axial nebeneinander angeordnet sind, wobei die Eingriffsteile (4a,4b,4c) der Aussenläufer (4,5)in Umfangs­richtung miteinander und in axialer Richtung mit denjenigen des benachbarten Aussenläufers (4,5) durch eine kreisring­förmige, axial innere Läuferscheibe (9) starr verbunden sind, so dass diese die Welle (12) der Innenläufer (2,3) um­schliesst und die Arbeitsräume der Maschine axial unterteilt, dadurch gekennzeichnet, dass der von der axial inneren Läu­ferscheibe (9) umschlossene Raum durch einen Trennwandkörper (15) ausgefüllt ist, wobei zwischen der Läuferscheibe(9) und dem Trennwandkörper (15) sowie zwischen diesem und der Welle 12) jeweils eine Lagerung (13,43) vorgesehen ist und Ar­beitsräume (16) der Maschine bis an den Trennwandkörper (15) heranreichen.1. internal-axis rotary piston machine with at least two fixed on a common shaft (12) inner rotors (2,3) and a corresponding number of external rotors (4,5) enclosed by a common housing (6) and are arranged axially next to each other, the Engaging parts (4a, 4b, 4c) of the outer rotor (4, 5) in the circumferential direction with one another and in the axial direction with those of the adjacent outer rotor (4, 5) are rigidly connected by an annular, axially inner rotor disk (9), so that these Shaft (12) encloses the inner rotor (2, 3) and axially divides the working spaces of the machine, characterized in that the space enclosed by the axially inner rotor disk (9) is filled by a partition wall body (15), with the rotor disk (9 ) and the partition body (15) and between this and the shaft 12) a bearing (13, 43) is provided and working spaces (16) of the machine up to the partition body (15) oak. 2. Rotationskolbenmaschine nach Anspruch 1, dadurch ge­kennzeichnet, dass die axial innere Läuferscheibe (9) mit dem Trennwandkörper (15) die Maschine in einen axial länge­ren Niederdruckteil (22) und einen axial kürzeren Hochdruck­teil (23) unterteilt, die über einen ausserhalb des Umfangs­gehäuses (6) verlaufenden Strömungskanal (21) miteinander verbunden sind.2. Rotary piston machine according to claim 1, characterized in that the axially inner rotor disk (9) with the partition wall body (15) divides the machine into an axially longer low-pressure part (22) and an axially shorter high-pressure part (23), which has an outside of the peripheral housing (6) extending flow channel (21) are interconnected. 3. Rotationskolbenmaschine nach Anspruch 1, dadurch ge­kennzeichnet, dass zwischen der Läuferscheibe (9) und dem Trennwandkörper (15) ein Wälzlager (13) und zwischen der Welle (12) und dem Trennwandkörper (15) ein Gleitlager (43) vorgesehen ist.3. Rotary piston machine according to claim 1, characterized in that a roller bearing (13) is provided between the rotor disk (9) and the partition wall body (15) and a slide bearing (43) is provided between the shaft (12) and the partition wall body (15). 4. Rotationskolbenmaschine nach Anspruch 1, dadurch ge­kennzeichnet, dass die axial einander benachbarten Aussen­bzw.Innenläufer (4,5;2,3) in Umfangsrichtung zueinander versetzt miteinander befestigt sind.4. Rotary piston machine according to claim 1, characterized in that the axially adjacent outer or inner rotor (4,5; 2,3) are attached to one another offset in the circumferential direction. 5. Rotationskolbenmaschine nach Anspruch 4, dadurch ge­kennzeichnet, dass die Versetzung 180° beträgt.5. Rotary piston machine according to claim 4, characterized in that the offset is 180 °.
EP89810265A 1988-04-15 1989-04-06 Internal axis rotary piston engine Expired - Lifetime EP0337950B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89810265T ATE78080T1 (en) 1988-04-15 1989-04-06 INBOARD ROTARY PISTON MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3812637 1988-04-15
DE3812637A DE3812637C1 (en) 1988-04-15 1988-04-15

Publications (3)

Publication Number Publication Date
EP0337950A2 true EP0337950A2 (en) 1989-10-18
EP0337950A3 EP0337950A3 (en) 1990-02-28
EP0337950B1 EP0337950B1 (en) 1992-07-08

Family

ID=6352095

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89810265A Expired - Lifetime EP0337950B1 (en) 1988-04-15 1989-04-06 Internal axis rotary piston engine

Country Status (5)

Country Link
US (1) US4960370A (en)
EP (1) EP0337950B1 (en)
JP (1) JPH01313601A (en)
AT (1) ATE78080T1 (en)
DE (2) DE3812637C1 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP2762675A1 (en) 2013-02-03 2014-08-06 Cornel Ciupan Internal combustion rotary engine

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US7186101B2 (en) 1998-07-31 2007-03-06 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle Engine
US7726959B2 (en) 1998-07-31 2010-06-01 The Texas A&M University Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US6386836B1 (en) 2000-01-20 2002-05-14 Eagle-Picher Industries, Inc. Dual gerotor pump for use with automatic transmission
DE10023010C2 (en) * 2000-05-11 2003-03-06 Peter Ingelheim Internal multi-lobe machine
KR100947687B1 (en) * 2002-02-05 2010-03-16 더 텍사스 에이 & 엠 유니버시티 시스템 Gerotor apparatus for a quasi-isothermal brayton cycle engine
US7663283B2 (en) 2003-02-05 2010-02-16 The Texas A & M University System Electric machine having a high-torque switched reluctance motor
EP1711685B1 (en) 2004-01-23 2015-09-16 Starrotor Corporation Gerotor apparatus for a quasi-isothermal brayton cycle engine
US7695260B2 (en) 2004-10-22 2010-04-13 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle engine
CZ302294B6 (en) * 2008-07-29 2011-02-09 Dvorák@Jirí Rotary-piston engine for compressible media
US9074524B2 (en) * 2011-12-09 2015-07-07 Eaton Corporation Air supply system with two-stage roots blower

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GB1284551A (en) * 1969-08-08 1972-08-09 Arthur E Brown Improvements in rotary positive-displacement fluid machines
DE2402621A1 (en) * 1974-01-21 1975-07-24 Ulrich Dipl Ing Rohs Rotary piston engine with rotor and blocking rotor - has housing with common combustion chamber for all working spaces
EP0167846A1 (en) * 1984-06-12 1986-01-15 Wankel, Felix, Dr. h.c. Internal axis rotary piston machine

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Publication number Priority date Publication date Assignee Title
EP2762675A1 (en) 2013-02-03 2014-08-06 Cornel Ciupan Internal combustion rotary engine

Also Published As

Publication number Publication date
JPH01313601A (en) 1989-12-19
ATE78080T1 (en) 1992-07-15
EP0337950B1 (en) 1992-07-08
US4960370A (en) 1990-10-02
EP0337950A3 (en) 1990-02-28
DE58901795D1 (en) 1992-08-13
DE3812637C1 (en) 1989-07-27

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