EP0167846B1 - Internal axis rotary piston machine - Google Patents

Internal axis rotary piston machine Download PDF

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Publication number
EP0167846B1
EP0167846B1 EP85107098A EP85107098A EP0167846B1 EP 0167846 B1 EP0167846 B1 EP 0167846B1 EP 85107098 A EP85107098 A EP 85107098A EP 85107098 A EP85107098 A EP 85107098A EP 0167846 B1 EP0167846 B1 EP 0167846B1
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EP
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Prior art keywords
rotor
internal
external
lateral faces
external rotor
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EP85107098A
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German (de)
French (fr)
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EP0167846A1 (en
Inventor
Felix Dr. H.C. Wankel
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Individual
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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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/14—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • 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 internal-axis rotary lobe machine with the features of the preamble of patent claim 1.
  • a machine of the type mentioned is known from US-A-1 753 476.
  • the inner rotor of this machine has semicircular circumferential surfaces, the radius of curvature of which, due to kinematics, is considerably smaller than that of the circular surface which encloses the outer rotor.
  • the inner rotor can only incompletely displace the medium from the recesses of the outer rotor.
  • An arc-shaped adaptation of the radially outer region of the recesses of the outer rotor to the circular peripheral surfaces of the inner rotor, in order to reduce the harmful spaces, in a form similar to that of a machine according to DE-A-2 46 252, would make the opening cross sections of the recesses even narrower to let.
  • the then crescent-shaped delimitation areas of the recesses would be subjected to bending deformations by centrifugal forces, and crushing currents would occur there to an increased extent.
  • the invention has for its object to find an improved machine of the type mentioned, which has a higher throughput due to the shape of their runners, based on their construction volume and very small harmful spaces and thereby enables high speeds of rotation of their runners.
  • the invention results in a cross-sectional shape of the rotor which enables high rotational speeds, although the inner rotor can move to the outer circumference of the outer rotor or even beyond in order to achieve very small, harmful spaces.
  • the machine according to the invention has surprisingly large working spaces in relation to the overall dimensions of the machine.
  • the side surfaces of the outer rotor that delimit the inner working spaces are preferably designed to be flat, wherein opposite inner side surfaces can advantageously run parallel to one another, so that large cross sections of the working spaces and large control openings on the outer rotor result.
  • outer corner regions of the inner rotor and the inner corner regions of the outer rotor are advantageously rounded off with a constant or variable cross-sectional curvature.
  • the inner corner areas of the outer rotor are guided radially inwards so that they come close to its shaft.
  • At least one adjustable wall piece which is provided on the inside of the housing and along which the circumference of the outer rotor moves, enables the delivery rate and / or the delivery pressure to be controlled by changing the time of inflow and thus the Size of the filling and / or the time of the outflow and thus the pressure level of the overflow in the pressure line changed.
  • a machine according to the invention can also be an internal combustion engine.
  • the cross-sectional view shows three main parts of the machine, i. H. an inner rotor 1, an outer rotor 2, with three rigidly connected rotor parts 2a, 2b and 2c and the housing 3 enclosing both of them.
  • the cross-sectional illustration in the illustration according to FIG. 1 visible boundary surfaces of these parts parallel to the axes of rotation of the rotor, while their invisible end boundary surfaces are perpendicular to these axes.
  • the wall of the housing 3 merges into an inflow and outflow channel 4, 5, it depending on the use of the machine whether the inflow channel 4 is an intake channel or an inflow channel for a propellant.
  • Both runners 1, 2 rotate about fixed axes 6, 7, which are spaced apart.
  • the speed ratio is 3: 2, corresponding to the ratio between the number of recesses 8, 9, 10 of the outer rotor forming working spaces to the number of engaging parts 11, 12 of the inner rotor extending from the axis 6.
  • this ratio is 4: 3, corresponding to four recesses 14, 15, 16, 17 and three parts 18, 19, 20 of the inner rotor that move into and out of the recesses.
  • the sequence of movements of the two runners 1, 2 relative to one another and relative to the machine housing 3 can be seen in the illustrations in FIG. 3.
  • the uninterrupted sealing between the inner and outer rotor results from the fact that both runners mutually create their shape when they move relative to each other.
  • the four outer corner regions 22-25 of the inner rotor according to FIG. 1 and the three inner corner regions 26, 27, 28 of the outer rotor are used for generating curves.
  • the corner regions of the inner rotor move or produce along the inner side surfaces 30, 31 of the outer rotor, and the inner corner regions 26, 27, 28 of the outer rotor move along or on the outer peripheral surfaces 32, 33 of the inner rotor generate these. This is illustrated by the movement positions shown in FIG.
  • the seal between the inner side surfaces 30, 31 of the outer rotor and the side surfaces 34, 35 of the inner rotor results from a tooth flank-like contact between the two.
  • the corner regions 22-28 of both runners are preferably rounded instead of sharp-edged, so that the rounding on the other rotor creates an equidistant to the center of curvature of the rounding.
  • the inner corner region 28 of the outer rotor 2 is relatively close to the axis of the inner rotor, as a comparison with the prior art according to the aforementioned DE-A-2 456 252 shows.
  • the throughput volume is, for example, 1 dm 3 .
  • the inner side surfaces 30, 31 of the outer rotor run parallel to one another, so that the opening of the recesses 8, 9, 10 of the outer rotor, which moves past the housing openings at a very high speed, is correspondingly advantageously large.
  • this opening cross section of the recesses of the outer rotor is advantageously large.
  • the exemplary embodiment according to FIG. 7 shows inner side surfaces of the outer rotor which run slightly towards one another radially outward.
  • the outer circumferential surfaces 32, 33 of the inner rotor move up to the outer circumference of the outer rotor, so that the harmful space results due to the different curvature of the circumferential surface of the inner rotor and the circumferential surface of the outer rotor. Since the outer circumferential surfaces 32, 33 of the inner rotor can also take over the sealing alone when passing through the sealing region 42 between the two channels 4, 5 of the housing, it is possible that these circumferential surfaces 32, 33 also move beyond the circumference of the outer rotor.
  • the seal between the outer rotor 2 and the housing inner wall on the side of the housing diametrically opposite the sealing area 42 between the channels 4, 5 is provided by means of a wall piece 43 which is adjustable in the circumferential direction, so that the internal compression of the machine can be changed from zero.
  • 1 shows a position of the wall piece 43 through which there is no internal compression, while in the position according to FIG. 2 the internal compression takes place up to the rotational position shown, until the working space 8 opens by the trailing edge 44 of the outer rotor away from the wall piece 43.
  • an actuating member not shown, which extends outwards through a slot in the housing wall.
  • Fig. 4 shows another embodiment for the design of means for the changes throughput and / or internal compression of the machine.
  • These means consist of a plurality of circular arc-shaped radial slides 46, 47 arranged next to one another in the circumferential direction on the inflow and outflow side of the machine when the rotor rotates in the direction of the arrow 48 an inflow takes place in the working space 8 'enclosed by both runners in the direction of arrow 49.
  • 4 shows two inflow-side radial slides 46 in a radially outer position, while the radial slides adjoining in the direction of rotation have their radially innermost position, so that maximum internal compression is achieved when the machine is operated as a compressor.
  • the strength of the internal compression can be gradually changed in this exemplary embodiment according to FIG. 4, corresponding to the number of radial slides 47 which are retracted radially outward from the position shown.
  • this means 43, 46, 47 for changing the delivery rate and / or the internal compression can be used on any machine in which there is an outer rotor rotating about a fixed axis, the recesses of which form radially outwardly open working spaces move past housing openings.
  • FIG. 6 shows how a machine according to the invention according to FIG. 7 can look in the axial cross section.
  • the parts of the machine according to FIGS. 6 and 7 already described with reference to FIG. 1 have the same reference numbers.
  • the parts 2a, 2b, 2c of the outer rotor are rigidly connected to one another at the two axial ends of the rotor by side plates 50, 51.
  • a hub 52 or 53 projects axially outward from these side plates, via which the outer rotor is mounted on the housing side plates 56, 57 by means of a ball bearing 54 or 55 of large diameter.
  • these bearings have extraordinarily high running speeds of the rolling elements, which can lead to premature wear, so that the above-mentioned embodiment according to their EP-A-0087747 by the same applicant is recommended.
  • the hub 53 of the outer rotor has an internal toothing 58 which meshes with a gearwheel 60 fastened on the shaft journal 59 of the inner rotor 1.
  • This existing drive connection is recommended for an exact run of the two runners to each other, so that there is always an optimal gap seal between the two runners, although the tooth-flank-like contact between the side surfaces of both runners could make the additional gear connection 58, 60 superfluous.
  • the side plates 50, 51 of the outer rotor enclose circular lateral sealing plates 62, 63 which are screwed onto the housing sides 56, 57 and which adjoin the end surfaces 64, 65 of the inner rotor with a sealing gap distance.
  • These sealing plates also enclose the two shaft journals 59, 66 of the inner rotor.
  • the outer bearing 44 of the outer rotor also encloses the roller bearing 67, 68 which supports the shaft journals 59, 66.
  • the on the shaft journal 59 of the inner rotor laterally protruding via the housing plate 57 gear 69 serves either to drive the machine when it is used as a blower or compressor or as an output gear when the machine as a motor or driver through an inflowing medium, such as . B. the exhaust gas of an internal combustion engine is driven.

Abstract

An internal axis single-rotation machine, wherein an external rotor and an internal rotor are mounted for intermeshing rotation about their own centers of gravity at different angular velocities within a casing and wherein two pairs of radially external sealing corner areas on the internal rotor kinematically describe internal lateral faces which define recesses in the external rotor and wherein internal sealing corner areas on the external rotor kinematically describe external peripheral faces on the internal rotor, the rotors being arranged in cooperating rotative relationship such that a meshing gear-like contact is maintained between the internal lateral faces of the external rotor and the lateral faces of the internal rotor.

Description

Die Erfindung betrifft eine innenachsige Drehkolbenmaschine mit den Merkmalen des Oberbegriffs des Patentanspruchs 1.The invention relates to an internal-axis rotary lobe machine with the features of the preamble of patent claim 1.

Eine Maschine der genannten Art ist bekannt durch die US-A-1 753 476. Der Innenläufer dieser Maschine hat halbkreisförmige Umfangsflächen, deren Krümmungsradius kinematisch bedingt wesentlich kleiner ist als derjenige der Kreisfläche, die den Aussenläufer einschliesst. Durch die somit vorhandenen schädlichen Räume kann der Innenläufer das Medium nur sehr unvollständig aus den Ausnehmungen des Aussenläufers herausverdrängen. Eine bogenförmige Anpassung des radial äusseren Bereichs der Ausnehmungen des Aussenläufers an die kreisförmigen Umfangsflächen des Innenläufers, um die schädlichen Räume zu verringern, in ähnlicher Form wie bei einer Maschine entsprechend der DE-A-2 46 252, würde die Oeffnungsquerschnitte der Ausnehmungen noch enger werden lassen. Ausserdem wären die dann sichelförmigen Begrenzungsbereiche der Ausnehmungen durch Zentrifugalkräfte Biegeverformungen ausgesetzt und es würden dort in verstärktem Masse Quetschströmungen auftreten.A machine of the type mentioned is known from US-A-1 753 476. The inner rotor of this machine has semicircular circumferential surfaces, the radius of curvature of which, due to kinematics, is considerably smaller than that of the circular surface which encloses the outer rotor. As a result of the harmful spaces thus present, the inner rotor can only incompletely displace the medium from the recesses of the outer rotor. An arc-shaped adaptation of the radially outer region of the recesses of the outer rotor to the circular peripheral surfaces of the inner rotor, in order to reduce the harmful spaces, in a form similar to that of a machine according to DE-A-2 46 252, would make the opening cross sections of the recesses even narrower to let. In addition, the then crescent-shaped delimitation areas of the recesses would be subjected to bending deformations by centrifugal forces, and crushing currents would occur there to an increased extent.

Der Erfindung liegt die Aufgabe zugrunde, eine verbesserte Maschine der eingangs genannten Art zu finden, die durch die Form ihrer Läufer einen höheren Durchsatz, bezogen auf ihr Bauvolumen sowie sehr kleine schädliche Räume aufweist und dabei hohe Drehgeschwindigkeiten ihrer Läufer ermöglicht. Diese Verbesserungen werden zusammen mit weiteren Vorteilen erfindungsgemäss durch eine Maschine mit den Merkmalen des Patentanspruchs 1 ermöglicht.The invention has for its object to find an improved machine of the type mentioned, which has a higher throughput due to the shape of their runners, based on their construction volume and very small harmful spaces and thereby enables high speeds of rotation of their runners. These improvements, together with further advantages, are made possible according to the invention by a machine with the features of patent claim 1.

Auf Grund der Erfindung ergibt sich eine Querschnittsform der Läufer, die hohe Drehgeschwindigkeiten ermöglicht, obwohl für die Erzielung sehr kleiner schädlicher Räume der Innenläufer sich bis an den Aussenumfang des Aussenläufers oder sogar darüber hinaus bewegen kann. Ausserdem weist die erfindungsgemässe Maschine überraschend grosse Arbeitsräume im Verhältnis zu den Gesamtabmessungen der Maschine auf.The invention results in a cross-sectional shape of the rotor which enables high rotational speeds, although the inner rotor can move to the outer circumference of the outer rotor or even beyond in order to achieve very small, harmful spaces. In addition, the machine according to the invention has surprisingly large working spaces in relation to the overall dimensions of the machine.

Die innere Arbeitsräume begrenzenden Seitenflächen des Aussenläufers sind vorzugsweise eben ausgebildet, wobei einander gegenüberliegende innere Seitenflächen vorteilhaft parallel zueinander verlaufen können, so dass sich grosse Querschnitte der Arbeitsräume und grosse Steueröffnungen am Aussenläufer ergeben.The side surfaces of the outer rotor that delimit the inner working spaces are preferably designed to be flat, wherein opposite inner side surfaces can advantageously run parallel to one another, so that large cross sections of the working spaces and large control openings on the outer rotor result.

Die äusseren Eckbereiche des Innenläufers und die inneren Eckbereiche des Aussenläufers sind vorteilhaft mit konstanter oder veränderlicher Querschnittskrümmung abgerundet.The outer corner regions of the inner rotor and the inner corner regions of the outer rotor are advantageously rounded off with a constant or variable cross-sectional curvature.

Zur Erzeugung grosser Arbeitsräume sind die inneren Eckbereiche des Aussenläufers weit radial nach innen geführt, so dass sie bis in die Nähe von dessen Welle gelangen.To create large working spaces, the inner corner areas of the outer rotor are guided radially inwards so that they come close to its shaft.

Mindestens ein verstellbares Wandstück, das an der Innenseite des Gehäuses vorgesehen ist, und an dem sich der Umfang des Aussenläufers entlang bewegt, ermöglicht in vorteilhafter Ausgestaltung der Erfindung eine Steuerung der Fördermenge und/oder des Förderdruckes, indem es den Zeitpunkt des Zuströmens und damit die Grösse der Füllung und/oder den Zeitpunkt der Abströmung und damit die Druckhöhe des Ueberschubes in die Druckleitung verändert.In an advantageous embodiment of the invention, at least one adjustable wall piece, which is provided on the inside of the housing and along which the circumference of the outer rotor moves, enables the delivery rate and / or the delivery pressure to be controlled by changing the time of inflow and thus the Size of the filling and / or the time of the outflow and thus the pressure level of the overflow in the pressure line changed.

Auf Grund der Erfindung ergeben sich Querschnittsformen des Aussen- und Innenläufers, die durch ihre hohe Festigkeit sehr hohe Drehgeschwindigkeiten zulassen und die sich mit Kühlkanälen versehen lassen, so dass die Maschine durch heisse Abgase angetrieben werden kann. Es versteht sich, dass bei entsprechender Ausgestaltung eine erfindungsgemässe Maschine auch eine Verbrennungskraftmaschine sein kann.On the basis of the invention, cross-sectional shapes of the outer and inner rotor result which, due to their high strength, permit very high rotational speeds and which can be provided with cooling channels, so that the machine can be driven by hot exhaust gases. It goes without saying that, with a corresponding configuration, a machine according to the invention can also be an internal combustion engine.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind der folgenden Beschreibung von Ausführungsbeispielen anhand der Zeichnungen entnehmbar. Es zeigen :

  • Fig. 1 und 2 ein erstes Ausführungsbeispiel der Drehkolbenmaschine im Radialquerschnitt mit verschiedenen Drehpositionen ihrer Läufer und verschiedenen Stellpositionen eines Wandstückes zur Veränderung der inneren Kompression,
  • Fig. 3a-1 eine Maschine entsprechend Fig. 1 und 2 ohne veränderliche innere Kompression mit mehreren aufeinanderfolgenden Drehpositionen ihrer Läufer,
  • Fig. 4 eine Ausführungsform der Maschine mit gleicher Ausbildung ihrer Läufer wie nach Fig. 1-3, jedoch mit einer anderen Ausführungsform von Mitteln zur Veränderung der Fördermenge und/ oder der inneren Kompression.
  • Fig. 5 einen Radialquerschnitt durch das Läuferpaar einer Maschine mit einem Drehzahlverhältnis von 4 : 3 und
  • Fig. 6 und 7 eine Maschine ohne innere Kompression im Axialquerschnitt entlang der Linie VI-VI und einem Radialquerschnitt.
Further advantageous embodiments of the invention can be found in the following description of exemplary embodiments with reference to the drawings. Show it :
  • 1 and 2 a first embodiment of the rotary piston machine in radial cross section with different rotational positions of its rotor and different positions of a wall piece for changing the internal compression,
  • 3a-1 a machine corresponding to FIGS. 1 and 2 without variable internal compression with several successive rotational positions of their runners,
  • Fig. 4 shows an embodiment of the machine with the same design of its rotor as in Fig. 1-3, but with a different embodiment of means for changing the delivery rate and / or the internal compression.
  • Fig. 5 shows a radial cross section through the rotor pair of a machine with a speed ratio of 4: 3 and
  • 6 and 7 a machine without internal compression in the axial cross section along the line VI-VI and a radial cross section.

Das Grundsätzliche einer erfindungsgemässen Maschine, das für alle ihre Ausführungsformen zutrifft, wird im folgenden anhand der Fig. 1 beschrieben.The basic principle of a machine according to the invention, which applies to all of its embodiments, is described below with reference to FIG. 1.

Die Querschnittsdarstellung lässt drei Hauptteile der Maschine erkennen, d. h. einen Innenläufer 1, einen Aussenläufer 2, mit drei starr miteinander verbundenen Läuferteilen 2a, 2b und 2c und das beide umschliessende Gehäuse 3. Wie auch der Querschnittsdarstellung eines Ausführungsbeispieles nach Fig. 6 entnehmbar ist, verlaufen die in der Darstellung nach Fig. 1 im Querschnitt sichtbaren Begrenzungsflächen dieser Teile parallel zu den Drehachsen der Läufer, während ihre nicht sichtbaren endseitigen Begrenzungsflächen senkrecht zu diesen Achsen verlaufen. Die Wand des Gehäuses 3 geht in einen Zuström- und Abströmkanal 4, 5 über, wobei es von der Verwendung der Maschine abhängt, ob der Zuströmkanal 4 ein Ansaugkanal ist oder ein Zuströmkanal für ein Treibmittel.The cross-sectional view shows three main parts of the machine, i. H. an inner rotor 1, an outer rotor 2, with three rigidly connected rotor parts 2a, 2b and 2c and the housing 3 enclosing both of them. As can also be seen from the cross-sectional illustration of an exemplary embodiment according to FIG. 6, the cross-sectional view in the illustration according to FIG. 1 visible boundary surfaces of these parts parallel to the axes of rotation of the rotor, while their invisible end boundary surfaces are perpendicular to these axes. The wall of the housing 3 merges into an inflow and outflow channel 4, 5, it depending on the use of the machine whether the inflow channel 4 is an intake channel or an inflow channel for a propellant.

Beide Läufer 1, 2 drehen sich um feststehende Achsen 6, 7, die einen Abstand voneinander aufweisen. Das Drehzahlverhältnis ist 3:2 entsprechend dem Verhältnis zwischen der Anzahl der Arbeitsräume bildenden Ausnehmungen 8, 9, 10 des Aussenläufers zu der Anzahl von sich von der Achse 6 wegerstreckenden Eingriffsteilen 11, 12 des Innenläufers.Both runners 1, 2 rotate about fixed axes 6, 7, which are spaced apart. The speed ratio is 3: 2, corresponding to the ratio between the number of recesses 8, 9, 10 of the outer rotor forming working spaces to the number of engaging parts 11, 12 of the inner rotor extending from the axis 6.

Im Beispiel nach Fig. 5 beträgt dieses Verhältnis 4:3, entsprechend vier Ausnehmungen 14, 15, 16, 17 und drei sich in die Ausnehmungen hinein und aus ihnen wieder herausbewegenden Teilen 18, 19, 20 des Innenläufers.In the example according to FIG. 5, this ratio is 4: 3, corresponding to four recesses 14, 15, 16, 17 and three parts 18, 19, 20 of the inner rotor that move into and out of the recesses.

Der Bewegungsablauf beider Läufer 1, 2 relativ zu einander und relativ zum Maschinengehäuse 3, ist den Darstellungen der Fig. 3 zu entnehmen. Die ununterbrochene Abdichtung zwischen dem Innen- und Aussenläufer ergibt sich dadurch, dass beide Läufer bei ihrer Bewegung relativ zueinander ihre Form gegenseitig erzeugen. Dabei werden die vier äusseren Eckbereiche 22-25 des Innenläufers nach Fig. 1 und die drei inneren Eckbereiche 26, 27, 28 des Aussenläufers zur Kurvenerzeugung verwendet. Beim vorgegebenen Drehzahlverhältnis zwischen beiden Läufem bewegen sich die Eckbereiche des Innenläufers entlang den inneren Seitenflächen 30, 31 des Aussenläufers bzw. erzeugen diese, und die inneren Eckbereiche 26, 27, 28 des Aussenläufers bewegen sich an den äusseren Umfangsflächen 32, 33 des Innenläufers entlang bzw. erzeugen diese. Dies ist durch die in Fig. gezeigten Bewegungspositionen veranschaulicht.The sequence of movements of the two runners 1, 2 relative to one another and relative to the machine housing 3 can be seen in the illustrations in FIG. 3. The uninterrupted sealing between the inner and outer rotor results from the fact that both runners mutually create their shape when they move relative to each other. The four outer corner regions 22-25 of the inner rotor according to FIG. 1 and the three inner corner regions 26, 27, 28 of the outer rotor are used for generating curves. At the predetermined speed ratio between the two rotors, the corner regions of the inner rotor move or produce along the inner side surfaces 30, 31 of the outer rotor, and the inner corner regions 26, 27, 28 of the outer rotor move along or on the outer peripheral surfaces 32, 33 of the inner rotor generate these. This is illustrated by the movement positions shown in FIG.

Die Abdichtung zwischen den inneren Seitenflächen 30, 31 des Aussenläufers und den Seitenflächen 34, 35 des Innenläufers ergibt sich durch eine zahnflankenartige Berührung zwischen beiden. Die Eckbereiche 22-28 beider Läufer sind vorzugsweise abgerundet statt scharfkantig, so dass die Abrundung am anderen Läufer eine Aequidistante zum Krümmungsmittelpunkt der Abrundung erzeugt.The seal between the inner side surfaces 30, 31 of the outer rotor and the side surfaces 34, 35 of the inner rotor results from a tooth flank-like contact between the two. The corner regions 22-28 of both runners are preferably rounded instead of sharp-edged, so that the rounding on the other rotor creates an equidistant to the center of curvature of the rounding.

Wie der in Fig. 1 dargestellten Drehposition zu entnehmen ist, befindet sich der innere Eckbereich 28 des Aussenläufers 2 verhältnismässig nahe zur Achse des Innenläufers, wie ein Vergleich mit dem Stand der Technik gemäss der genannten DE-A-2 456 252 zeigt. Daraus ergibt sich der in Fig. 1 sichtbare ausserordentlich grosse Querschnitt des Raumes zwischen den inneren Seitenflächen 30, 31 des Aussenläufers, der Seitenfläche 34 des Innenläufers und der inneren Gehäuseflächen 37, so dass das Durchsatzvolumen der Maschine im Verhältnis zu ihrer Baugrösse besonders gross ist. Bei einer Baugrösse von beispielsweise 1,35 dm3 beträgt das Durchsatzvolumen beispielsweise 1 dm3.As can be seen from the rotational position shown in FIG. 1, the inner corner region 28 of the outer rotor 2 is relatively close to the axis of the inner rotor, as a comparison with the prior art according to the aforementioned DE-A-2 456 252 shows. This results in the extraordinarily large cross section of the space visible in FIG. 1 between the inner side surfaces 30, 31 of the outer rotor, the side surface 34 of the inner rotor and the inner housing surfaces 37, so that the throughput volume of the machine is particularly large in relation to its size. With a size of, for example, 1.35 dm 3 , the throughput volume is, for example, 1 dm 3 .

Die inneren Seitenflächen 30, 31 des Aussenläufers verlaufen im Beispiel nach Fig. 1 parallel zueinander, so dass die Oeffnung der Ausnehmungen 8, 9, 10 des Aussenläufers, die sich jeweils mit sehr hoher Geschwindigkeit an den Gehäuseöffnungen vorbeibewegt, entsprechend vorteilhaft gross ist. Auch bei den übrigen Ausführungsbeispielen ist dieser Oeffnungsquerschnitt der Ausnehmungen des Aussenläufers vorteilhaft gross. Das Ausführungsbeispiel nach Fig. 7 zeigt innere Seitenflächen des Aussenläufers, die radial nach aussen leicht aufeinander zulaufen.In the example according to FIG. 1, the inner side surfaces 30, 31 of the outer rotor run parallel to one another, so that the opening of the recesses 8, 9, 10 of the outer rotor, which moves past the housing openings at a very high speed, is correspondingly advantageously large. In the other exemplary embodiments, too, this opening cross section of the recesses of the outer rotor is advantageously large. The exemplary embodiment according to FIG. 7 shows inner side surfaces of the outer rotor which run slightly towards one another radially outward.

Trotz dieser besonders grossen äusseren Oeffnungsquerschnitte der Ausnehmungen 8, 9, 10 des Aussenläufers wird das genannte besonders grosse Arbeitsvolumen zwischen den inneren Seitenflächen des Aussenläufers bei der Bewegung des Innenläufers in diesen Ausnehmungen 8, 9, 10 hinein nahezu vollständig verdrängt, wie die Drehposition entsprechend Fig. 3a zeigt. Auf diese Weise ist nahezu kein schädliches Volumen vorhanden, das bei der Ausführungsform der Maschine als Kompressor von dem Druckkanal 5 zurück zu dem Saugkanal 4 gefördert wird. Dieses schädliche Volumen ist in Fig. 3a mit den Ziffern 40, 41 bezeichnet. Die negative Auswirkung dieses schädlichen Volumens ist jedoch vemachlässigbar, nicht nur weil es besonders klein ist, sondern weil das darin komprimierte Medium Arbeitsleistung erbringt, da es auf die Läufer in Drehrichtung wirkt, wie Fig. 3a veranschaulicht.Despite these particularly large outer opening cross-sections of the recesses 8, 9, 10 of the outer rotor, the particularly large working volume mentioned between the inner side surfaces of the outer rotor is almost completely displaced into these recesses 8, 9, 10 when the inner rotor moves, as is the rotational position according to FIG 3a shows. In this way, there is almost no harmful volume that is conveyed back from the pressure channel 5 to the suction channel 4 in the embodiment of the machine as a compressor. This harmful volume is designated by the numbers 40, 41 in FIG. 3a. However, the negative impact of this harmful volume is negligible, not only because it is particularly small, but because the medium compressed therein performs work because it acts on the rotor in the direction of rotation, as illustrated in FIG. 3a.

Im dargestellten Ausführungsbeispiel bewegen sich die äusseren Umfangsflächen 32, 33 des Innenläufers bis an den äusseren Umfang des Aussenläufers heran, so dass sich der schädliche Raum auf Grund der unterschiedlichen Krümmung der Umfangsfläche des Innenläufers und der Umfangsfläche des Aussenläufers ergibt. Da die äusseren Umfangsflächen 32, 33 des Innenläufers beim Passieren des dichtenden Bereiches 42 zwischen beiden Kanälen 4, 5 des Gehäuses auch allein die Abdichtung übernehmen können, ist es möglich, dass diese Umfangsflächen 32, 33 sich auch über den Umfang des Aussenläufers hinausbewegen.In the exemplary embodiment shown, the outer circumferential surfaces 32, 33 of the inner rotor move up to the outer circumference of the outer rotor, so that the harmful space results due to the different curvature of the circumferential surface of the inner rotor and the circumferential surface of the outer rotor. Since the outer circumferential surfaces 32, 33 of the inner rotor can also take over the sealing alone when passing through the sealing region 42 between the two channels 4, 5 of the housing, it is possible that these circumferential surfaces 32, 33 also move beyond the circumference of the outer rotor.

Die Abdichtung zwischen dem Aussenläufer 2 und der Gehäuseinnenwand auf der dem Dichtbereich 42 zwischen den Kanälen 4, 5 diametral gegenüberliegenden Seite des Gehäuses erfolgt mittels eines in Umfangsrichtung verstellbaren Wandstückes 43, so dass die innere Kompression der Maschine ausgehend von Null veränderbar ist. Die Fig. 1 zeigt eine Position des Wandstückes 43, durch die sich keine innere Kompression ergibt, während in der Position nach Fig.2 die innere Kompression bis zur dargestellten Drehposition erfolgt, bis sich der Arbeitsraum 8 öffnet, indem die nachlaufende Kante 44 des Aussenläufers sich von dem Wandstück 43 entfernt. Für die Verstellung des Wandstückes 43 in Umfangsrichtung ist ein nicht dargestelltes Betätigungsorgan vorhanden, das sich durch einen Schlitz in der Gehäusewand nach aussen erstreckt. Durch Verstellen des Wandstückes 43, ausgehend von der Position nach Fig. 1 in Richtung zu dem Zuströmkanal 4, lässt sich ausserdem die Durchsatzmenge ändern, da auf diese Weise der Winkelbereich der Umdrehung des Aussenläufers verkleinert wird, innerhalb dessen Medium in den sich zunehmend vergrössernden Arbeitsraum 8 zwischen beiden Läufern einströmen kann.The seal between the outer rotor 2 and the housing inner wall on the side of the housing diametrically opposite the sealing area 42 between the channels 4, 5 is provided by means of a wall piece 43 which is adjustable in the circumferential direction, so that the internal compression of the machine can be changed from zero. 1 shows a position of the wall piece 43 through which there is no internal compression, while in the position according to FIG. 2 the internal compression takes place up to the rotational position shown, until the working space 8 opens by the trailing edge 44 of the outer rotor away from the wall piece 43. For the adjustment of the wall piece 43 in the circumferential direction, there is an actuating member, not shown, which extends outwards through a slot in the housing wall. By adjusting the wall piece 43, starting from the position according to FIG. 1 in the direction of the inflow channel 4, the throughput quantity can also be changed, since in this way the angular range of the rotation of the external rotor is reduced, within the medium of which in the increasingly larger working space 8 can flow between the two runners.

Die Fig. 4 zeigt ein anderes Ausführungsbeispiel für die Ausgestaltung von Mitteln für die Veränderung des Durchsatzvolumens und/oder der inneren Kompression der Maschine. Diese Mittel bestehen aus mehreren in Umfangsrichtung nebeneinander angeordneten kreisbogenförmigen Radialschiebem 46, 47 auf der Zuström- und Abströmseite der Maschine bei Drehrichtung der Läufer in Richtung des Pfeiles 48. Die zuströmseitigen Radialschieber verändern die Grösse des sich an den Zuströmkanal 4' anschliessenden Bogenbereich, über den eine Zuströmung in den von beiden Läufern eingeschlossenen Arbeitsraum 8' in Richtung des Pfeiles 49 erfolgt. Die Fig. 4 zeigt zwei zuströmseitige Radialschieber 46 in radial äusserer Position, während die in Drehrichtung sich anschliessenden Radialschieber ihre radial innerste Position haben, so dass beim Betrieb der Maschine als Kompressor eine maximale innere Kompression erreicht wird. Die Stärke der inneren Kompression lässt sich bei diesem Ausführungsbeispiel nach Fig. 4 stufenweise verändern, entsprechend der Anzahl der aus der dargestellten Position radial nach aussen zurückgezogenen Radialschieber 47.Fig. 4 shows another embodiment for the design of means for the changes throughput and / or internal compression of the machine. These means consist of a plurality of circular arc-shaped radial slides 46, 47 arranged next to one another in the circumferential direction on the inflow and outflow side of the machine when the rotor rotates in the direction of the arrow 48 an inflow takes place in the working space 8 'enclosed by both runners in the direction of arrow 49. 4 shows two inflow-side radial slides 46 in a radially outer position, while the radial slides adjoining in the direction of rotation have their radially innermost position, so that maximum internal compression is achieved when the machine is operated as a compressor. The strength of the internal compression can be gradually changed in this exemplary embodiment according to FIG. 4, corresponding to the number of radial slides 47 which are retracted radially outward from the position shown.

Es versteht sich, dass dieses Mittel 43, 46, 47 zur Veränderung der Fördermenge und/oder der inneren Kompression an jeder Maschine anwendbar ist, bei der eine sich um eine feststehende Achse drehender Aussenläufer vorhanden ist, dessen radial nach aussen offenen Arbeitsräume bildenden Aussparungen sich an Gehäuseöffnungen vorbeibewegen.It goes without saying that this means 43, 46, 47 for changing the delivery rate and / or the internal compression can be used on any machine in which there is an outer rotor rotating about a fixed axis, the recesses of which form radially outwardly open working spaces move past housing openings.

Die Fig. 6 zeigt, wie eine erfindungsgemässe Maschine gemäss Fig. 7 im Axialquerschnitt aussehen kann. Die bereits anhand der Fig. 1 beschriebenen Teile der Maschine nach Fig. 6 und 7 haben die gleichen Bezugsziffern.FIG. 6 shows how a machine according to the invention according to FIG. 7 can look in the axial cross section. The parts of the machine according to FIGS. 6 and 7 already described with reference to FIG. 1 have the same reference numbers.

Die Teile 2a, 2b, 2c des Aussenläufers sind an den beiden axialen Enden des Läufers durch Seitenplatten 50, 51 starr miteinander verbunden. Von diesen Seitenplatten steht axial nach aussen eine Nabe 52 bzw. 53 ab, über die der Aussenläufer mittels eines Kugellagers 54 bzw. 55 von grossem Durchmesser an den Gehäuseseitenplatten 56, 57 gelagert ist. Bei hohen Drehgeschwindigkeiten ergeben sich an diesen Lagern ausserordentlich hohe Laufgeschwindigkeiten der Wälzkörper, die zu vorzeitigem Verschleiss führen können, so dass sich die erwähnte Ausführung gemäss deren EP-A-0087747 des gleichen Anmelders empfiehlt.The parts 2a, 2b, 2c of the outer rotor are rigidly connected to one another at the two axial ends of the rotor by side plates 50, 51. A hub 52 or 53 projects axially outward from these side plates, via which the outer rotor is mounted on the housing side plates 56, 57 by means of a ball bearing 54 or 55 of large diameter. At high rotational speeds, these bearings have extraordinarily high running speeds of the rolling elements, which can lead to premature wear, so that the above-mentioned embodiment according to their EP-A-0087747 by the same applicant is recommended.

Auf der An- bzw. Abtriebsseite der Maschine hat die Nabe 53 des Aussenläufers eine Innenverzahnung 58, die mit einem auf dem Wellenzapfen 59 des Innenläufers 1 befestigten Zahnrad 60 kämmt. Diese somit vorhandene Antriebsverbindung empfiehlt sich für einen exakten Lauf beider Läufer zueinander, so dass eine optimale Spaltdichtung zwischen beiden Läufern stets vorhanden ist, obwohl die zahnflankenartige Berührung zwischen den Seitenflächen beider Läufer die zusätzliche Zahnradverbindung 58, 60 überflüssig machen könnte.On the input or output side of the machine, the hub 53 of the outer rotor has an internal toothing 58 which meshes with a gearwheel 60 fastened on the shaft journal 59 of the inner rotor 1. This existing drive connection is recommended for an exact run of the two runners to each other, so that there is always an optimal gap seal between the two runners, although the tooth-flank-like contact between the side surfaces of both runners could make the additional gear connection 58, 60 superfluous.

Die Seitenplatten 50, 51 des Aussenläufers umschliessen kreisförmige seitliche Dichtplatten 62, 63, die an den Gehäuseseiten 56, 57 angeschraubt sind und mit dichtendem Spaltabstand an die Endflächen 64, 65 des Innenläufers angrenzen. Diese Dichtplatten umschliessen ausserdem die beiden Wellenzapfen 59, 66 des Innenläufers. Entsprechend umschliesst auch das äussere Lager 44 des Aussenläufers jeweils das die Wellenzapfen 59, 66 lagernde Wälzlager 67, 68.The side plates 50, 51 of the outer rotor enclose circular lateral sealing plates 62, 63 which are screwed onto the housing sides 56, 57 and which adjoin the end surfaces 64, 65 of the inner rotor with a sealing gap distance. These sealing plates also enclose the two shaft journals 59, 66 of the inner rotor. Correspondingly, the outer bearing 44 of the outer rotor also encloses the roller bearing 67, 68 which supports the shaft journals 59, 66.

Das auf dem Wellenzapfen 59 des Innenläufers befestigte seitlich über die Gehäuseplatte 57 herausragende Zahnrad 69 dient entweder dem Antrieb der Maschine, wenn diese als Gebläse oder Kompressor verwendet wird oder als Abtriebszahnrad, wenn die Maschine als Motor bzw. Treiber durch ein zuströmendes Medium, wie z. B. das Abgas einer Verbrennungskraftmaschine angetrieben wird.The on the shaft journal 59 of the inner rotor laterally protruding via the housing plate 57 gear 69 serves either to drive the machine when it is used as a blower or compressor or as an output gear when the machine as a motor or driver through an inflowing medium, such as . B. the exhaust gas of an internal combustion engine is driven.

Claims (8)

1. Internal axis single-rotation machine with an external rotor (2) sealingly surrounded by a common casing (3) and an internal rotor (1), which are in each case formed by at least one engagement part (2a, 2b, 2c; 11, 12) with lateral faces (30, 31 ; 34, 35) and circumferential faces (32, 33) and which in the case of a tooth flank-like contact between the lateral faces (30, 31) of the external rotor (2) and the lateral faces (34, 35) of the internal rotor (1) uniformly rotate with a speed ratio of n + 1 : n, whereby between the engagement parts (2a, 2b, 2c) of the external rotor (2) are located n + 1 recesses (8, 9, 10), which are radially open to the outside and bounded by said lateral faces (30, 31) for the engagement of n, i. e. at least one engagement part (11, 12) of the internal rotor (1) and the n + 1 recesses (8, 9, 10) forming the working spaces move past inlets and outlets (4, 5) provided in the casing circumference, characterized in that a continuously sealing engagement between the two rotors (1, 2) is obtained in that the inner lateral faces (30, 31) of the engagement parts (2a, 2b, 2c) of the external rotor (2) form pairwise radially inner corner regions (26, 27, 28), which are curve generating for external circumferential faces (32, 33) of internal rotor (1) and that these circumferential faces (32, 33) form with the circumferentially adjacent lateral face (34, 35) of the at least one engagement part (11, 12) of the internal rotor (1) radially external corner regions (22-25) which are curve generating of the inner lateral faces (30, 31) of the external rotor (2).
2. Single-rotation machine according to claim 1, characterized in that the inner lateral faces (30, 31) of the external rotor (2) are planar.
3. Single-rotation machine according to claim 2, characterized in that the facing inner lateral faces (30, 31) of the external rotor (2) are parallel to one another.
4. Single-rotation machine according to one of the claims 1 to 3, characterized in that the curve generating corner regions (22-28) or rotors (2, 1) are rounded with a constant or variable curvature.
5. Single-rotation machine according to one of the claims 1 to 4, characterized in that the radially inner corner regions (26, 27, 28) of the external rotor (2) extend into the vicinity of the shaft (59, 66) of the internal rotor (1).
6. Single-rotation machine according to one of the claims 1 to 5, characterized in that the engagement parts (11, 12) of the internal rotor (1) penetrate into said recesses (8, 9, 10) at least up to the circumference of the external rotor (2).
7. Single-rotation machine according to one of the claims 1 to 6, characterized in that for modifying the through-feed rate and/or the pressure level of a transfer in a pressure line (5) between the circumference of the external rotor (2) and the casing inner wall are provided a plurality of circumferentially juxtaposed and radially individually adjustable wall portions (46, 47).
EP85107098A 1984-06-12 1985-06-08 Internal axis rotary piston machine Expired - Lifetime EP0167846B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85107098T ATE51432T1 (en) 1984-06-12 1985-06-08 INBOARD ROTARY LOBE MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2822/84 1984-06-12
CH2822/84A CH664423A5 (en) 1984-06-12 1984-06-12 INNER AXIS ROTARY PISTON.

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EP0167846A1 EP0167846A1 (en) 1986-01-15
EP0167846B1 true EP0167846B1 (en) 1990-03-28

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US (2) US4714417A (en)
EP (1) EP0167846B1 (en)
JP (1) JPH0612045B2 (en)
AT (1) ATE51432T1 (en)
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DE (2) DE3432915A1 (en)

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Also Published As

Publication number Publication date
DE3576839D1 (en) 1990-05-03
DE3432915A1 (en) 1985-12-12
US4801255A (en) 1989-01-31
DE3432915C2 (en) 1987-01-02
CH664423A5 (en) 1988-02-29
JPH0612045B2 (en) 1994-02-16
JPS614802A (en) 1986-01-10
EP0167846A1 (en) 1986-01-15
US4714417A (en) 1987-12-22
ATE51432T1 (en) 1990-04-15

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