EP0087747B1 - Internal-axis rotary-piston machine without crank-shaft - Google Patents

Internal-axis rotary-piston machine without crank-shaft Download PDF

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Publication number
EP0087747B1
EP0087747B1 EP83101746A EP83101746A EP0087747B1 EP 0087747 B1 EP0087747 B1 EP 0087747B1 EP 83101746 A EP83101746 A EP 83101746A EP 83101746 A EP83101746 A EP 83101746A EP 0087747 B1 EP0087747 B1 EP 0087747B1
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EP
European Patent Office
Prior art keywords
shaft
rotor
bearing
rotary piston
piston engine
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Expired
Application number
EP83101746A
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German (de)
French (fr)
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EP0087747A3 (en
EP0087747A2 (en
Inventor
Felix Dr. H.C. Wankel
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Individual
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Individual
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Priority to AT83101746T priority Critical patent/ATE19900T1/en
Publication of EP0087747A2 publication Critical patent/EP0087747A2/en
Publication of EP0087747A3 publication Critical patent/EP0087747A3/en
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Publication of EP0087747B1 publication Critical patent/EP0087747B1/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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • 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
    • F01C1/104—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 one member having simultaneously a rotational movement about its own axis and an orbital movement
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/10—Rotary-piston pumps specially adapted for elastic fluids 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

Definitions

  • the invention relates to an inner-axis crankshaft-free rotary piston machine with two eccentrically mounted rotors, the circularly curved raceway of the bearing of the outer rotor enclosing the shaft of the inner rotor.
  • Rotary piston machines of the type mentioned are known, for example, from US-A-724 665, US-A-3 954 355 and GB-A-961 872.
  • the design principle of a machine of the type mentioned at the outset inevitably entails that the raceway of the two bearings of the outer rotor has a relatively large diameter, since it surrounds the shaft of the inner rotor arranged eccentrically to it, if both rotors are not only disadvantageously be stored on one side.
  • the bearings of the rotors of the known machines mentioned are designed as slide bearings, so that they have only a small dimension in the radial direction.
  • the relatively large diameter of the bearing of the outer rotor results in correspondingly high bearing speeds, so that the known machines are only suitable for relatively low rotational speeds and have relatively high friction losses.
  • the use of conventional roller bearings for the bearing of the outer rotor would lead to a structurally disadvantageous increase in the radial dimension of the bearing or to a further increase in the bearing race.
  • the speed of rotation of the machine would also be relatively limited, since the large diameter of the raceway would lead to a correspondingly high speed of rotation of the rolling bearing bodies.
  • the present invention is based on the object of avoiding the disadvantages of the known machines, so that they can be operated at significantly higher rotational speeds and thus can be used in small dimensions for new applications, e.g. as a loader or driver of an internal combustion engine.
  • the invention is based on the further object of being able to arrange the shaft of the inner rotor relative to the outer rotor with greater eccentricity and / or to be able to give it a larger diameter.
  • the shaft of the inner rotor can be arranged between such bearing devices so that it is located radially further out.
  • the shaft itself can form one of the bearing devices by rolling the bearing race on the circumference of the shaft or on a ring surrounding the shaft.
  • the bearing devices preferably consist of rollers that can be supported by ball bearings.
  • the bearing of the outer rotor is preferably arranged in the axial direction of the machine between its runners and a drive connection between the runners, the individual bearing devices being carried by a sealing body which is rigidly connected to a fixed outer machine housing and in the bearing raceway of the outer rotor enclosed space extends up to the side surface of the inner rotor and is sealed radially from the outer rotor. Because the sealing body thus provides a radial seal with respect to the outer rotor or the annular space formed by the usual hollow gear of the outer rotor is avoided, it is not necessary for the side face of the inner rotor to cover such a cavity in every movement position by a suitable size of the inner rotor and thus seals to the working area of the machine.
  • the arrangement of the drive connection between the two rotors in the axial direction, given by a pinion engaging in a ring gear, or the arrangement of the bearing in the axial direction between the drive connection and the inner rotor has the further advantage that the cavity of the outer rotor for the passage of the shaft of the Inner rotor can be made smaller in diameter than the diameter of the hollow gear of the outer rotor.
  • the shaft diameter of the inner rotor can advantageously be chosen larger by arranging the shaft between two bearing devices arranged next to one another in the circumferential direction.
  • this does not allow the shaft diameter to be increased at the point at which the pinion of the drive connection between the two runners is provided, because the diameter of the pinion is determined by the eccentricity between the two runners and the required transmission ratio.
  • the drive transmission between this pinion and the hollow gear of the outer rotor takes place via two intermediate gears or an intermediate annular gear with an internal and external teeth. It is understood that in this case the hollow gear of the external rotor is to be made larger in diameter.
  • the present invention can be advantageously used with all rotary piston machines of the type mentioned at the outset, since the inner-axis construction requires an outer rotor which has a relatively large bearing race in diameter, so that correspondingly high speeds occur in this race.
  • the storage devices in the form of rollers can also be used, e.g. individual magnetic bearings, individual air cushion bearings, etc.
  • the support rollers can also be used for the lateral guidance of the external rotor, i.e. they can also absorb forces acting on the outer rotor in the axial direction if they are provided with a wheel flange or a groove which interacts with a groove or a wheel flange of the raceway of the outer rotor.
  • the inner rotor 4 has a circular cross section and rotates in an eccentric movement about the main shaft 6 of the machine, which only rotates about its own axis.
  • the shaft 6 is supported by two roller bearings 9, 10 in sealing bodies 13, 14 which are rigidly connected to the side housing covers 11, 12.
  • a second bearing 15, 16 provided on the outer circumference of the sealing bodies 14, 13 serves to mount the outer rotor 18 about its central axis, which is thus fixed locally. Due to the large diameter of these bearings 15, 16 and the relatively small diameter of the rolling elements of these bearings, the latter are exposed to high rolling speeds and thus high loads, which should be avoided according to the present invention.
  • a seal 20, 21 between the side walls 26, 27 of the extension 18 facing the working space 22 of the machine and the part 19 of the sealing body 13, 14 protruding into it prevents the bearings 9, 10, 15, 16 and a drive transmission 23 between the Internal and external rotors can disadvantageously come into contact with the medium flowing through the machine. The throughflow takes place through the nozzles 7, 8 attached radially on the outside of the machine housing.
  • the outer rotor 18 enclosing the inner rotor 4 consists of two crescent-shaped peripheral parts 24, 25 lying opposite one another and two side parts 26, 27 enclosing them between one another , so that the inner rotor can execute a reciprocating movement in the working space 22 delimited by these surfaces.
  • This relatively straight-line movement of the inner rotor 4 relative to the outer rotor 18 despite the rotary movement of both rotors results from the kinematics of gimbals.
  • the inner rotor 4 which can also be referred to as a rotary piston, comes into meshing engagement with two gaps in the outer rotor so that it rotates at twice the speed of the outer rotor.
  • the gear ratio accordingly corresponds to 1: 2, so that the pitch circle of the pinion 34 of the drive transmission 23 between the inner and outer rotor has half the diameter of the pitch circle of the hollow gear 35.
  • FIGS. 5-7 show, however, that the ratio of 1: 2 can also be achieved in other ways.
  • the shaft for cooling the inner rotor 4 as shown in FIG Fig. 8 can be made hollow and / or for a greater axial length of the rotor receives a higher strength, can according to the schematic representations of FIGS.
  • FIG. 3 and 4 show an embodiment according to the invention in that the outer rotor 18 'is supported by three rollers 52, 53, 54 which are themselves mounted on the sealing body 14'. Two of the rollers (52, 53) are supported by a bearing pin 56 in the sealing body 14 ', while the third is supported on the shaft 6.
  • These rollers 52 to 54 made of hardened material roll on a bearing ring 58 made of hardened steel, which is inserted into a lateral hub part 60 of the outer rotor.
  • a lateral end face of the hollow gear 62 secures the axial position of this bearing ring 58.
  • the immediate arrangement of the bearing ring 58 and the bearing rollers 52 to 54 rolling thereon ensures a good lubrication by the lubricant supplied to the gear.
  • a ring 54 can also be firmly attached to the shaft if its diameter is equal to the pitch circle diameter of the pinion 34, so that at the speed ratio of 1: 2 a slip-free rolling on the radially inner tread of the Bearing ring 58 takes place.
  • a sealing ring 66 is provided which ensures the sealing of the part of the machine provided with lubricant together with the seal 20 on the sealing body 14'.
  • the rollers 52-54 can be provided with a web or wheel flange which is small in cross-section and which engages in a correspondingly shaped groove in the bearing ring 58, so that there is guidance against axial displacement between the shaft and the external rotor is.

Abstract

An internal axis crankless rotary piston engine with an internal rotor and an external rotor mounted eccentrically to one another, with a circularly curved path of the external rotor mounting surrounding an internal rotor shaft, wherein the path of an external rotor bearing is mounted by a plurality of bearings which are spaced from one another in the direction of movement and which are fixed relative to the geometrical axis of the internal rotor shaft.

Description

Die Erfindung betrifft eine innenachsige kurbelwellenlose Rotationskolbenmaschine mit zwei zueinander exzentrisch gelagerten Läufern, wobei die kreisförmig gekrümmte Laufbahn der Lagerung des Aussenläufers die Welle des Innenläufers umschliesst.The invention relates to an inner-axis crankshaft-free rotary piston machine with two eccentrically mounted rotors, the circularly curved raceway of the bearing of the outer rotor enclosing the shaft of the inner rotor.

Rotationskolbenmaschinen der genannten Art sind beispielsweise durch die US-A- 724 665, US-A-3 954 355 und die GB-A-961 872 bekannt. Das Konstruktionsprinzip bei einer Maschine der eingangs genannten Art, bringt es zwangsläufig mit sich, dass die Laufbahn der beiden Lager des Aussenläufers einen verhältnismässig grossen Durchmesser aufweist, da sie die exzentrisch zu ihr angeordnete Welle des Innenläufers umschliesst, falls beide Läufer nicht auf nachteilige Weise nur einseitig gelagert werden. Die Lager der Läufer der genannten bekannten Maschinen sind als Gleitlager ausgebildet, so dass sie in radialer Richtung nur eine geringe Abmessung aufweisen. Durch den verhältnismässig grossen Durchmesser des Lagers des Aussenläufers entstehen entsprechend hohe Lagergeschwindigkeiten, so dass die bekannten Maschinen nur für verhältnismässig geringe Drehgeschwindigkeiten geeignet sind und verhältnismässig hohe Reibungsverluste aufweisen. Die Verwendung üblicher Wälzlager für die Lagerung des Aussenläufers würde zu einer konstruktiv nachteiligen Vergrösserung der radialen Abmessung des Lagers führen bzw. zu einer weiteren Vergrösserung der Laufbahn der Lagerung. Ausserdem wäre die Drehgeschwindigkeit der Maschine ebenfalls verhältnismässig begrenzt, da der grosse Durchmesser der Laufbahn zu entsprechend hoher Drehgeschwindigkeit der Wälzlagerkörper führen würde.Rotary piston machines of the type mentioned are known, for example, from US-A-724 665, US-A-3 954 355 and GB-A-961 872. The design principle of a machine of the type mentioned at the outset inevitably entails that the raceway of the two bearings of the outer rotor has a relatively large diameter, since it surrounds the shaft of the inner rotor arranged eccentrically to it, if both rotors are not only disadvantageously be stored on one side. The bearings of the rotors of the known machines mentioned are designed as slide bearings, so that they have only a small dimension in the radial direction. The relatively large diameter of the bearing of the outer rotor results in correspondingly high bearing speeds, so that the known machines are only suitable for relatively low rotational speeds and have relatively high friction losses. The use of conventional roller bearings for the bearing of the outer rotor would lead to a structurally disadvantageous increase in the radial dimension of the bearing or to a further increase in the bearing race. In addition, the speed of rotation of the machine would also be relatively limited, since the large diameter of the raceway would lead to a correspondingly high speed of rotation of the rolling bearing bodies.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, die genannten Nachteile der bekannten Maschinen zu vermeiden, so dass sie mit wesentlich höheren Drehgeschwindigkeiten betrieben werden kann und somit bei kleinen Abmessungen neuen Anwendungsbereichen zugeführt werden kann, z.B. als Lader oder Treiber einer Verbrennungskraftmaschine. In konstruktiver Hinsicht liegt der Erfindung die weitere Aufgabe zugrunde, die Welle des Innenläufers relativ zum Aussenläufer mit grösserer Exzentrizität anordnen zu können und/oder ihr einen grösseren Durchmesser geben zu können. Die Lösung dieser Aufgaben erfolgt dadurch, dass die Laufbahn der Lagerung des Aussenläufers durch mehrere in Laufrichtung einen Abstand voneinander aufweisende Lagereinrichtungen gelagert ist, die relativ zur geometrischen Achse der Welle des Innenläufers ortsfest angeordnet sind.The present invention is based on the object of avoiding the disadvantages of the known machines, so that they can be operated at significantly higher rotational speeds and thus can be used in small dimensions for new applications, e.g. as a loader or driver of an internal combustion engine. In design terms, the invention is based on the further object of being able to arrange the shaft of the inner rotor relative to the outer rotor with greater eccentricity and / or to be able to give it a larger diameter. These tasks are solved in that the bearing path of the bearing of the outer rotor is supported by a plurality of bearing devices which are spaced apart in the running direction and which are arranged in a stationary manner relative to the geometric axis of the shaft of the inner rotor.

Durch die erfindungsgemässe Anordnung mehrerer Lagereinrichtungen in Laufrichtung nebeneinander, kann die Welle des Innenläufers zwischen solchen Lagereinrichtungen angeordnet werden, so dass sie sich radial weiter aussen befindet. Dabei kann die Welle selbst eine der Lagereinrichtungen bilden, indem sich die Laufbahn des Lagers am Umfang der Welle oder auf einem die Welle umschliessenden Ring abwälzt. Die Lagereinrichtungen bestehen vorzugsweise aus Rollen, die durch Kugellager gelagert sein können.By arranging several bearing devices next to one another in the running direction according to the invention, the shaft of the inner rotor can be arranged between such bearing devices so that it is located radially further out. The shaft itself can form one of the bearing devices by rolling the bearing race on the circumference of the shaft or on a ring surrounding the shaft. The bearing devices preferably consist of rollers that can be supported by ball bearings.

Vorzugsweise ist die Lagerung des Aussenläufers in axialer Richtung der Maschine zwischen ihren Läufern und einer Antriebsverbindung zwischen den Läufern angeordnet, wobei die einzelnen Lagereinrichtungen von einem Abdichtkörper getragen sind, der mit einem feststehenden äusseren Maschinengehäuse starr verbunden ist und sich in den von der Laufbahn der Lagerung des Aussenläufers umschlossenen Raum hinein bis an die Seitenfläche des Innenläufers erstreckt und radial gegenüber dem Aussenläufer abgedichtet ist. Dadurch, dass somit der Abdichtkörper eine radiale Abdichtung gegenüber dem Aussenläufer bewirkt bzw. der durch das übliche Hohlzahnrad des Aussenläufers gebildete Ringraum vermieden wird, ist es nicht notwendig, dass die Seitenfläche des Innenläufers durch geeignete Grösse des Innenläufers in jeder Bewegungsposition einen solchen Hohlraum überdeckt und somit zum Arbeitsraum der Maschine hin abdichtet. Die Anordnung der durch ein in ein Hohlzahnrad eingreifendes Ritzel gegebenen Antriebsverbindung zwischen beiden Läufern in axialer Richtung aussen bzw. die Anordnung der Lagerung in axialer Richtung zwischen der Antriebsverbindung und dem Innenläufer hat den weiteren Vorteil, dass der Hohlraum des Aussenläufers für die Hindurchführung der Welle des Innenläufers im Durchmesser kleiner ausgeführt sein kann als der Durchmesser des Hohlzahnrades des Aussenläufers.The bearing of the outer rotor is preferably arranged in the axial direction of the machine between its runners and a drive connection between the runners, the individual bearing devices being carried by a sealing body which is rigidly connected to a fixed outer machine housing and in the bearing raceway of the outer rotor enclosed space extends up to the side surface of the inner rotor and is sealed radially from the outer rotor. Because the sealing body thus provides a radial seal with respect to the outer rotor or the annular space formed by the usual hollow gear of the outer rotor is avoided, it is not necessary for the side face of the inner rotor to cover such a cavity in every movement position by a suitable size of the inner rotor and thus seals to the working area of the machine. The arrangement of the drive connection between the two rotors in the axial direction, given by a pinion engaging in a ring gear, or the arrangement of the bearing in the axial direction between the drive connection and the inner rotor has the further advantage that the cavity of the outer rotor for the passage of the shaft of the Inner rotor can be made smaller in diameter than the diameter of the hollow gear of the outer rotor.

Wie bereits erwähnt, kann der Wellendurchmesser des Innenläufers durch die Anordnung der Welle zwischen zwei in Umfangsrichtung nebeneinander angeordneten Lagereinrichtungen vorteilhaft grösser gewählt werden. Dies ermöglicht jedoch dabei nicht gleichzeitig die Vergrösserung des Wellendurchmessers an der Stelle, an der das Ritzel der Antriebsverbindung zwischen beiden Läufern vorgesehen ist, denn der Durchmesser des Ritzels ist durch die Exzentrizität zwischen beiden Läufern und das erforderliche Uebersetzungsverhältnis bestimmt. Um dennoch auch an dieser Stelle die Welle im Durchmesser grösser ausbilden zu können, z.B. um sie als Hohlwelle für die Kühlung des Innenläufers auszuführen, erfolgt die Antriebsübertragung zwischen diesem Ritzel und dem Hohlzahnrad des Aussenläufers über zwei zwischengeschaltete Zahnräder oder ein zwischengeschaltetes ringförmiges Zahnrad mit Innen- und Aussenverzahnung. Es versteht sich, dass in diesem Fall das Hohlzahnrad des Aussenläufers entsprechend im Durchmesser grösser auszubilden ist.As already mentioned, the shaft diameter of the inner rotor can advantageously be chosen larger by arranging the shaft between two bearing devices arranged next to one another in the circumferential direction. However, this does not allow the shaft diameter to be increased at the point at which the pinion of the drive connection between the two runners is provided, because the diameter of the pinion is determined by the eccentricity between the two runners and the required transmission ratio. In order to be able to make the shaft larger in diameter at this point, for example, to design it as a hollow shaft for cooling the inner rotor, the drive transmission between this pinion and the hollow gear of the outer rotor takes place via two intermediate gears or an intermediate annular gear with an internal and external teeth. It is understood that in this case the hollow gear of the external rotor is to be made larger in diameter.

Es versteht sich, dass die vorliegende Erfindung bei allen Rotationskolbenmaschinen der eingangs genannten Art vorteilhaft anwendbar ist, da die innenachsige Bauweise einen Aussenläufer voraussetzt, der eine im Durchmesser verhältnismässig grosse Laufbahn der Lagerung aufweist, so dass entsprechend hohe Geschwindigkeiten an dieser Laufbahn auftreten.It goes without saying that the present invention can be advantageously used with all rotary piston machines of the type mentioned at the outset, since the inner-axis construction requires an outer rotor which has a relatively large bearing race in diameter, so that correspondingly high speeds occur in this race.

Statt der erwähnten Ausführungsmöglichkeit der Lagereineinrichtungen in Form von Rollen können auch andersartige Lagereinrichtungen verwendet werden, wie z.B. einzelne Magnetlager, einzelne Luftkissenlager usw. Die Stützrollen können auch für die seitliche Führung des Aussenläufers verwendet werden, d.h. sie können auch in axialer Richtung auf den Aussenläufer wirkende Kräfte aufnehmen, falls sielkit einem Spurkranz oder einer Rille versehen sind, der mit einer Rille oder einem Spurkranz der Laufbahn des Aussenläufers zusammenwirkt.Instead of the mentioned possibility of executing the storage devices in the form of rollers, other types of storage devices can also be used, e.g. individual magnetic bearings, individual air cushion bearings, etc. The support rollers can also be used for the lateral guidance of the external rotor, i.e. they can also absorb forces acting on the outer rotor in the axial direction if they are provided with a wheel flange or a groove which interacts with a groove or a wheel flange of the raceway of the outer rotor.

Im folgenden wird die Erfindung anhand zeichnerischer Darstellungen näher erläutert. Es zeigt:

  • Fig. 1 einen radial verlaufenden Querschnitt durch eine Rotationskolbenmaschine,
  • Fig. 2 einen Axialschnitt durch die Maschine nach Fig. 1 mit einem Abdichtkörper, jedoch mit einer nicht erfindungsgemässen Lagerung des Aussenläufers,
  • Fig. 3 einen axialen Teilquerschnitt durch eine Rotationskolbenmaschine mit einer erfindungsgemässen Lagerung entlang der Linie 111 - 111 der Fig. 4,
  • Fig. 4 einen Radialquerschnitt entlang der Linie IV-IV der Fig. 3,
  • Fig. 5 & 6 schematische Darstellungen von zwei Ausführungsbeispielen einer Antriebsverbindung zwischen Innen- und Aussenläufer,
  • Fig. 7 einen axialen Teilschnitt zu der Antriebsverbindung nach Fig. 6 und
  • Fig. 8 einen Querschnitt durch einen mit einer Luftkühlung versehenen Innenläufer.
The invention is explained in more detail below with the aid of drawings. It shows:
  • 1 is a radial cross section through a rotary piston machine,
  • 2 shows an axial section through the machine according to FIG. 1 with a sealing body, but with a bearing of the external rotor not according to the invention,
  • 3 shows an axial partial cross section through a rotary piston machine with a bearing according to the invention along the line 111-111 of FIG. 4,
  • 4 shows a radial cross section along the line IV-IV of FIG. 3,
  • 5 & 6 are schematic representations of two embodiments of a drive connection between the inner and outer rotor,
  • Fig. 7 is a partial axial section to the drive connection of FIG. 6 and
  • Fig. 8 shows a cross section through an internal rotor provided with air cooling.

Fig. 1 zeigt eine innenachsige Drehkolbenmaschine 2, die aufgrund der Erfindung besonders als Treiber und/oder Lader einer Verbrennungskraftmaschine geeignet ist. Der Innenläufer 4 hat einen kreisrunden Querschnitt und dreht sich in exzentrischer Bewegung um die sich nur um ihre eigene Achse drehende Hauptwelle 6 der Maschine. Die Welle 6 ist im dargestellten Beispiel durch zwei Wälzlager 9, 10 in starr mit den seitlichen Gehäusedeckeln 11, 12 verbundenen Abdichtkörpern 13, 14 gelagert. Durch die Drehung des Innenläufers 4 um die örtlich fixierte Welle 6 kann er in sich vollkommen ausgewuchtet werden, so dass auf die Lagerung keine Zentrifugalkräfte einwirken und somit sehr hohe Drehgeschwindigkeiten möglich sind.1 shows an internal-axis rotary lobe machine 2 which, owing to the invention, is particularly suitable as a driver and / or charger of an internal combustion engine. The inner rotor 4 has a circular cross section and rotates in an eccentric movement about the main shaft 6 of the machine, which only rotates about its own axis. In the example shown, the shaft 6 is supported by two roller bearings 9, 10 in sealing bodies 13, 14 which are rigidly connected to the side housing covers 11, 12. By rotating the inner rotor 4 around the locally fixed shaft 6, it can be completely balanced, so that no centrifugal forces act on the bearing and very high rotational speeds are therefore possible.

Jeweils ein am äusseren Umfang der Abdichtkörper 14, 13 vorgesehenes zweites Lager 15, 16 dient der Lagerung des Aussenläufers 18 um seine damit örtlich fixierte Mittelachse. Aufgrund des grossen Durchmessers dieser Lager 15, 16 und des verhältnismässig kleinen Durchmessers der Wälzkörper dieser Lager, sind letztere hohen Abwälzgeschwindigkeiten und damit hohen Belastungen ausgesetzt, die gemäss der vorliegenden Erfindung vermieden werden sollen. Eine Dichtung 20, 21 zwischen den dem Arbeitsraum 22 der Maschine zugekehrten Seitenwänden 26, 27 des Ausläufers 18 und dem in diese hineinragenden Teil 19 der Abdichtkörper 13, 14 verhindert, dass die Lagerungen 9, 10, 15, 16 und eine Antriebsübertragung 23 zwischen dem Innen- und Aussenläufer mit dem die Maschine durchströmenden Medium auf nachteilige Weise in Kontakt gelangen können. Die Durchströmung erfolgt durch die radial aussen am Maschinengehäuse angesetzten Stutzen 7, 8.In each case a second bearing 15, 16 provided on the outer circumference of the sealing bodies 14, 13 serves to mount the outer rotor 18 about its central axis, which is thus fixed locally. Due to the large diameter of these bearings 15, 16 and the relatively small diameter of the rolling elements of these bearings, the latter are exposed to high rolling speeds and thus high loads, which should be avoided according to the present invention. A seal 20, 21 between the side walls 26, 27 of the extension 18 facing the working space 22 of the machine and the part 19 of the sealing body 13, 14 protruding into it prevents the bearings 9, 10, 15, 16 and a drive transmission 23 between the Internal and external rotors can disadvantageously come into contact with the medium flowing through the machine. The throughflow takes place through the nozzles 7, 8 attached radially on the outside of the machine housing.

Der den Innenläufer 4 einschliessende Aussenläufer 18 besteht aus zwei einander gegenüberliegenden sichelförmigen Umfangsteilen 24, 25 und zwei diese zwischen sich einschliessenden Seitenteilen 26, 27. Die Verbindung untereinander erfolgt durch Stifte 28 und Schraubenbolzen 29. Die zueinandergerichteten Innenflächen 30, 32 des Aussenläufers verlaufen parallel zueinander, so dass der Innenläufer in dem durch diese Flächen begrenzten Arbeitsraum 22 eine hin- und hergehende Bewegung ausführen kann. Diese relativ gesehen geradlinige Bewegung des Innenläufers 4 relativ zum Aussenläufer 18 trotz der Drehbewegung beider Läufer ergibt sich aufgrund der Kinematik von Kardankreisen. Der auch als Drehkolben zu bezeichnende Innenläufer 4 gelangt in Kämmeingriff jeweils mit zwei Lücken des Aussenläufers, so dass er sich mit doppelter Geschwindigkeit des Aussenläufers dreht. Das Uebersetzungsverhältnis entspricht demnach 1:2, so dass der Teilkreis des Ritzels 34 der Antriebsübertragung 23 zwischen Innen- und Aussenläufer den halben Durchmesser des Teilkreises des Hohlzahnrades 35 aufweist. Die Figuren 5 - 7 zeigen jedoch, dass das Uebersetzungsverhältnis von 1:2 auch auf andere Weise erreicht werden kann. Um bei gleichem Abstand der Achse der Welle 6 von der Achse des Aussenläufers und bei gleichem Uebersetzungverhältnis einen grösseren Durchmesser der Welle 6 und einen entsprechend grösseren Durchmesser des Ritzels 34 verwirklichen zu können, so dass die Welle für die Kühlung des Innenläufers 4 entsprechend der Darstellung in Fig. 8 hohl ausgeführt werden kann und/oder für eine grössere axiale Länge der Läufer eine höhere Festigkeit erhält, können entsprechend den schematischen Darstellungen der Fig. 5 und 6 zwischen dem Ritzel 34', 34" und dem äusseren Hohlzahnrad 35', 35" mindestens zwei Zwischenzahnräder angeordnet werden. Im Beispiel nach Fig. 5 erfolgt die Antriebsübertragung zwischen dem Ritzel und dem Hohlzahnrad über zwei verschieden grosse Zwischenzahnräder 42, 43, während im Beispiel nach Fig. 6 zwischen dem Ritzel 34" und dem Hohlzahnrad 35" ein mit einer Innen- und Aussenverzahnung versehenes Höhlzahnrad 45 angeordnet ist. Dieses Hohlzahnrad 45.ist über ein Lager 46 relativ zum Gehäuseder Maschine oder einem mit dem Gehäuse verbundenen Teil 47 gelagert, wie der axiale Teilquerschnitt nach Fig. 7 zeigt. Es versteht sich, dass die Lagerung 46 nach dem gleichen Prinzip ausgeführt sein kann, wie die Lagerung des Aussenläufers entsprechend den Darstellungen der Fig. 3 und 4, wobei dann die Rollen im Gehäuseteil 47 zu lagern wären.The outer rotor 18 enclosing the inner rotor 4 consists of two crescent-shaped peripheral parts 24, 25 lying opposite one another and two side parts 26, 27 enclosing them between one another , so that the inner rotor can execute a reciprocating movement in the working space 22 delimited by these surfaces. This relatively straight-line movement of the inner rotor 4 relative to the outer rotor 18 despite the rotary movement of both rotors results from the kinematics of gimbals. The inner rotor 4, which can also be referred to as a rotary piston, comes into meshing engagement with two gaps in the outer rotor so that it rotates at twice the speed of the outer rotor. The gear ratio accordingly corresponds to 1: 2, so that the pitch circle of the pinion 34 of the drive transmission 23 between the inner and outer rotor has half the diameter of the pitch circle of the hollow gear 35. FIGS. 5-7 show, however, that the ratio of 1: 2 can also be achieved in other ways. In order to be able to realize a larger diameter of the shaft 6 and a correspondingly larger diameter of the pinion 34 with the same distance between the axis of the shaft 6 and the axis of the outer rotor and with the same transmission ratio, so that the shaft for cooling the inner rotor 4 as shown in FIG Fig. 8 can be made hollow and / or for a greater axial length of the rotor receives a higher strength, can according to the schematic representations of FIGS. 5 and 6 between the pinion 34 ', 34 "and the outer ring gear 35', 35" at least two intermediate gears are arranged. In the example according to FIG. 5, the drive transmission between the pinion and the ring gear takes place via two intermediate gears 42, 43 of different sizes, while in the example according to FIG. 6 between the pinion 34 "and the ring gear 35" one with an internal and Hollow gear 45 provided with external teeth is arranged. This ring gear 45 is supported via a bearing 46 relative to the housing of the machine or a part 47 connected to the housing, as the axial partial cross section according to FIG. 7 shows. It goes without saying that the mounting 46 can be designed according to the same principle as the mounting of the external rotor according to the illustrations in FIGS. 3 and 4, in which case the rollers in the housing part 47 would then have to be mounted.

Die Darstellungen der Fig. 3 und 4 zeigen ein Ausführungsbeispiel gemäss der Erfindung, indem die Lagerung des Aussenläufers 18'durch drei Rollen 52, 53, 54 erfolgt, die selbst an dem Abdichtkörper 14' gelagert sind. Zwei der Rollen (52, 53) sind durch einen Lagerzapfen 56 in dem Abdichtkörper 14'gelagert, während die dritte auf der Welle 6 gelagert ist. Diese aus gehärtetem Material bestehenden Rollen 52 bis 54 wälzen sich auf einem aus gehärtetem Stahl bestehendem Lagerring 58 ab, der in einen seitlichen Nabenteil 60 des Aussenläufers eingesetzt ist. Eine seitliche Stirnfläche des Hohlzahnrades 62 sichert die axiale Lage dieses Lagerringes 58. Die unmittelbare Anordnung des Lagerringes 58 und der sich an ihm abwälzenden Lagerrollen 52 bis 54 neben dem Zahngetriebe 23' gewährleistet eine gute Schmierung durch das dem Getriebe zugeführte Schmiermittel. Statt einer auf der Welle 6' angeordneten Rolle 54 kann auf der Welle auch ein Ring 54 fest aufgebracht sein, falls ihr Durchmesser gleich dem Teilkreisdurchmesser des Ritzelz 34 ist, so dass beim Drehzahlverhältnis von 1 : 2 eine schluppfreie Abwälzung auf der radial inneren Lauffläche des Lagerringes 58 erfolgt.3 and 4 show an embodiment according to the invention in that the outer rotor 18 'is supported by three rollers 52, 53, 54 which are themselves mounted on the sealing body 14'. Two of the rollers (52, 53) are supported by a bearing pin 56 in the sealing body 14 ', while the third is supported on the shaft 6. These rollers 52 to 54 made of hardened material roll on a bearing ring 58 made of hardened steel, which is inserted into a lateral hub part 60 of the outer rotor. A lateral end face of the hollow gear 62 secures the axial position of this bearing ring 58. The immediate arrangement of the bearing ring 58 and the bearing rollers 52 to 54 rolling thereon ensures a good lubrication by the lubricant supplied to the gear. Instead of a roller 54 arranged on the shaft 6 ', a ring 54 can also be firmly attached to the shaft if its diameter is equal to the pitch circle diameter of the pinion 34, so that at the speed ratio of 1: 2 a slip-free rolling on the radially inner tread of the Bearing ring 58 takes place.

Zwischen dem äusseren Umfang des den Lagerring 58 tragenden Nabenteiles 60 des Aussenläufers 18' und dem seitlichen Gehäusenteil 65 ist ein Dichtring 66 vorgesehen, der die Abdichtung des mit Schmiermittel versehen Teiles der Maschine zusammen mit der Dichtung 20 an dem Abdichtkörper 14' gewährleistet.Between the outer circumference of the hub part 60 of the outer rotor 18 'which carries the bearing ring 58 and the lateral housing part 65, a sealing ring 66 is provided which ensures the sealing of the part of the machine provided with lubricant together with the seal 20 on the sealing body 14'.

In nicht dargestellter Weise können die Rollen 52 - 54 mit einem im Querschnitt Kleinen umlaufenden Steg bzw. Spurkranz versehen sein, der in eine entsprechend geformte Rille in dem Lagerring 58 eingreift, so dass eine Führung gegen eine axiale Verschiebung zwichen der Welle und dem Aussenläufer gegeben ist.In a manner not shown, the rollers 52-54 can be provided with a web or wheel flange which is small in cross-section and which engages in a correspondingly shaped groove in the bearing ring 58, so that there is guidance against axial displacement between the shaft and the external rotor is.

Claims (8)

1. An internally axed crankless rotary piston engine with two rotors mounted eccentrically to one another, the circularly curved path of the external rotor mounting surrounding the internal rotor shaft, characterized in that the path (58) of the bearing of the external rotor (18') is mounted by a plurality of bearing means (52,53,54) which are spaced from one another in the direction of movement and which are fixed relativ to the geometrical axis of the shaft (6') of the internal rotor (4.).
2. A rotary piston engine according to claim 1, characterized in that the shaft (6') of the internal rotor (4') is circumferentially arranged between two bearing means.
3. A rotary piston engine according to claim 1, characterized in that the bearing means are rollers (52,53,54), which roll on the bearing path (58) of the external rotor (18').
4. A rotary piston engine according to claim 3, characterized in that the shaft (6') of the internal rotor (4') carries one of the bearing means (54), the path (58) of the external rotor (18') rolling on the circumference of the shaft (6') or on a ring (54) surrounding said shaft.
5. A rotary piston engine according to one of the claims 1 to 4, characterized in that the bearing of the external rotor (18') in the axial direction of the engine is arranged between the internal rotor (4') and a driving connection (23') between the rotors, individual bearing means (52, 53) being carried by a sealing member (14'), which is rigidly connected to a fixed outer engine casing (65) and extends into the space surrounded by the bearing path (58) of the external rotor (18') and up to the lateral surface of the internal rotor (4') and has a radial sealing (20') with respect to the external rotor (18').
6. A rotary piston engine according to one of the claims 1 to 5, characterized in that the driving connection (23') between both rotors (4' 18') has a hollow gear (35', 35"), the shaft (6') of the internal rotor (4') carrying a pinion (34, 34', 34"), which is in driving connection with the hollow gear, either directly or via one ore more intermediate gears (figs. 5 and 6).
7. A rotary piston engine according to one of the claims 1 to 6, characterized in that the internal rotor (4') has a cavity for air cooling purposes and which forms a flow duct together with the hollow journal (6') of the rotor.
8. A rotary piston engine according to claim 3, characterized in that the rollers (52, 53, 54) of the bearing means or the bearing path (58) of the external rotor (18') has a flange, which engages in the path (58) or rollers (52, 53, 54).
EP83101746A 1982-03-03 1983-02-23 Internal-axis rotary-piston machine without crank-shaft Expired EP0087747B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83101746T ATE19900T1 (en) 1982-03-03 1983-02-23 INNER AXLE CRANKSHAFTLESS ROTARY PISTON ENGINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1302/82 1982-03-03
CH1302/82A CH664193A5 (en) 1982-03-03 1982-03-03 EXHAUST-ROTATED PISTON LOADER.

Publications (3)

Publication Number Publication Date
EP0087747A2 EP0087747A2 (en) 1983-09-07
EP0087747A3 EP0087747A3 (en) 1984-05-09
EP0087747B1 true EP0087747B1 (en) 1986-05-21

Family

ID=4207255

Family Applications (2)

Application Number Title Priority Date Filing Date
EP83101745A Withdrawn EP0087746A1 (en) 1982-03-03 1983-02-23 Rotary piston supercharger driven by exhaust gases
EP83101746A Expired EP0087747B1 (en) 1982-03-03 1983-02-23 Internal-axis rotary-piston machine without crank-shaft

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP83101745A Withdrawn EP0087746A1 (en) 1982-03-03 1983-02-23 Rotary piston supercharger driven by exhaust gases

Country Status (6)

Country Link
US (1) US4540356A (en)
EP (2) EP0087746A1 (en)
JP (3) JPS58180701A (en)
AT (1) ATE19900T1 (en)
CH (1) CH664193A5 (en)
DE (1) DE3363572D1 (en)

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CH667491A5 (en) * 1985-08-31 1988-10-14 Wankel Felix INNER AXIS ROTARY PISTON.
KR920700352A (en) * 1989-03-31 1992-02-19 원본미기재 Rotary piston compressor
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KR100516506B1 (en) * 2004-12-11 2005-09-26 (주)힘틀 Rotary pump
CZ302294B6 (en) * 2008-07-29 2011-02-09 Dvorák@Jirí Rotary-piston engine for compressible media
TR200805753A2 (en) * 2008-08-04 2009-03-23 Yaşar Tuncer Yilmaz Rotary internal combustion engine
DE102009040051B4 (en) * 2009-09-03 2014-05-08 Siemens Aktiengesellschaft Free piston machine with magnetic bearing of the piston
DE102014209864A1 (en) * 2014-05-23 2015-12-17 Bayerische Motoren Werke Aktiengesellschaft Load control element for a quantity-controlled internal combustion engine
RU2664725C1 (en) * 2017-05-12 2018-08-22 Михаил Владимирович Давыдов Rotary piston engine

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Also Published As

Publication number Publication date
JPS58180701A (en) 1983-10-22
DE3363572D1 (en) 1986-06-26
JPS58180724A (en) 1983-10-22
US4540356A (en) 1985-09-10
EP0087747A3 (en) 1984-05-09
ATE19900T1 (en) 1986-06-15
EP0087747A2 (en) 1983-09-07
JPS58180728A (en) 1983-10-22
CH664193A5 (en) 1988-02-15
JPH0325602B2 (en) 1991-04-08
EP0087746A1 (en) 1983-09-07

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