EP0218806B1 - Internal-axis rotary piston machine - Google Patents

Internal-axis rotary piston machine Download PDF

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Publication number
EP0218806B1
EP0218806B1 EP86109613A EP86109613A EP0218806B1 EP 0218806 B1 EP0218806 B1 EP 0218806B1 EP 86109613 A EP86109613 A EP 86109613A EP 86109613 A EP86109613 A EP 86109613A EP 0218806 B1 EP0218806 B1 EP 0218806B1
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EP
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Prior art keywords
sealing
sealing gaps
rotors
circumferential surfaces
internal rotor
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EP86109613A
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German (de)
French (fr)
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EP0218806A1 (en
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Otto Kraic
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Individual
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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
    • F01C1/00—Rotary-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
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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 according to the preamble of claim 1.
  • Such a machine shows e.g. GB-A 316 295.
  • the dimensioning of the sealing gaps between the two runners represents an unsatisfactory compromise between the size of the sealing losses and the friction losses, whereby small sealing gaps, in addition to correspondingly high friction losses, also place high demands on the dimensionally accurate manufacture and assembly.
  • the object of the invention is to improve this compromise in a machine of this type by achieving a good seal between the rotors of the machine with relatively small losses at the sealing gaps. This object is achieved on the basis of the characterizing features of patent claim 1.
  • the improved compromise is based on the different evaluation of the different surface areas of the inner rotor when forming the sealing gap together with the outer rotor in order to seal the pressure side of the rotary piston machine from its side of low pressure, both with regard to the shape of the sealing gap or the surfaces forming it and also with regard to the meaning the local and temporal respective sealing gap position during the rotation of the rotor forming the sealing gap.
  • the outer circumference 4 of the outer rotor 2 surrounds the axis 5 of the inner rotor 3, which is fixed relative to the machine housing 1, and the axes 5, 6 of both rotors 2, 3 are arranged at a distance from one another.
  • the mutual arrangement of the rotors 2, 3 or their axes 5, 6 is consequently comparable to that on a gear with an internally toothed spur gear.
  • both runners 2 , 3 are located at a plurality of sealing points or sealing areas Di, D 2 , D 3 , D 4 , Ds. .. in a gap-forming approach to one another, and along two mutually opposite circumferential regions 10, 11 is the outer circumference 4 of the engagement parts 2a, 2b, 2c of the outer rotor and / or the outer circumference 12 of the engagement parts 3a, 3b of the inner rotor 2 in a gap-forming approach on the inner surface of the machine housing 1.
  • This approximation or the width of these sealing gaps is, depending on the manufacturing quality or depending on the application of the machine or on the density of the medium flowing through the machine, in the order of magnitude of, for example, 0.05 to 0.1 mm.
  • both runners 2, 3 are in drive connection via gear wheels 26, 27, one of which is formed on the inside of the hub-shaped hollow journal 19 by an internal toothing.
  • the gearwheel 28, which is placed on the outside of the shaft journal 15 of the inner rotor 3, is used for driving or driving, depending on whether the machine is driven by a gas flow or promotes it as a compressor.
  • the actual width of the sealing gaps is, for example, 0.05 mm at the narrowest sealing gaps manufactured by manufacture and, for example, 0.1 mm at the widest sealing joints manufactured by manufacture.
  • the sealing gaps D 4 occurring in the area of the radially inner circumferential surfaces 32, 33 of the inner rotor 3 during the rotation of the rotor also have to separate the low and high pressure sides of the machine from one another, but there can be wider sealing gaps D 4 to reduce frictional losses are accepted, since in this area the surfaces of both runners 2, 3 adjacent to the sealing gap are located at a short distance from one another and thus contribute to the sealing, or widen the sealing gap in the circumferential direction.
  • Larger or further sealing gaps on the radially inner circumferential surfaces 32, 33 provide the further advantage of reducing losses due to squeezing currents, in particular when the machine is intended for high rotational speeds of, for example, more than 20,000 rpm.
  • Fig. 4 shows the corresponding embodiment.
  • narrower sealing gaps D 4 are preferably also provided on the radially inner circumferential surfaces 32, 33 of the inner rotor in order to obtain a good seal, as the exemplary embodiment in FIG. 5 shows.
  • the sealing gaps D which occur with respect to the inner surfaces 35,36 of the engagement parts 2a, 2b, 2c are wider in each embodiment according to the invention than in the region of the radial outer peripheral surfaces 12a, 12b, so that the friction losses occurring there are correspondingly low. This is possible without significant sealing losses, since these sealing gaps D i , D 2, in accordance with the representations of the rotational positions in FIGS.
  • the width of the sealing gap Di, D 2 can advantageously be increasingly larger, corresponding to their distance from the axis 5 of the inner rotor, as shown in FIGS. 5 and 6, so that the undersize to be provided for the corresponding sealing gap widths on the inner or outer rotor increases radially outwards.

Abstract

For an improved sealing at the sealing gaps of a single-rotation machine having internal axes and accompanied by minimum frictionally losses, the width of the sealing gaps is made to differ in such a way that the narrower sealing gaps occur on the radially outer circumferential surfaces of the internal rotor facing the engagement parts of the external rotor. The comparatively wider sealing gaps occur on the transition surfaces between radially inner circumferential surfaces and radially outer circumferential surfaces of the internal rotor.

Description

Die Erfindung betrifft eine innenachsige Drehkolbenmaschine gemäss dem Oberbegriff des Patentanspruchs 1. Eine derartige Maschine zeigt z.B. die GB-A 316 295.The invention relates to an internal-axis rotary lobe machine according to the preamble of claim 1. Such a machine shows e.g. GB-A 316 295.

Bei bekannten Maschinen dieser Art stellt die Bemessung der Dichtspalte zwischen beiden Läufern einen unbefriedigenden Kompromiss zwischen der Grösse der Dichtverluste und der Reibungsverluste dar, wobei kleine Dichtspalte neben entsprechend hohen Reibungsverlusten auch hohe Anforderungen an die massgenaue Herstellung und Montage mit sich bringen. Die Erfindung liegt die Aufgabe zugrunde, bei einer Maschine dieser Art diesen Kompromiss zu verbessern, indem bei verhätnismässig geringen Verlusten an den Dichtspalten eine gute Abdichtung zwischen den Läufern der Maschine erzielt wird. Die Lösung dieser Aufgabe erfolgt aufgrund der kennzeichnenden Merkmale des Patentanspruchs 1.In known machines of this type, the dimensioning of the sealing gaps between the two runners represents an unsatisfactory compromise between the size of the sealing losses and the friction losses, whereby small sealing gaps, in addition to correspondingly high friction losses, also place high demands on the dimensionally accurate manufacture and assembly. The object of the invention is to improve this compromise in a machine of this type by achieving a good seal between the rotors of the machine with relatively small losses at the sealing gaps. This object is achieved on the basis of the characterizing features of patent claim 1.

Der verbesserte Kompromiss beruht auf der unterschiedlichen Bewertung der verschiedenen Oberflächenbereiche des Innenläufers bei ihrer Dichtspaltbildung zusammen mit dem Aussenläufer, um die Druckseite der Drehkolbenmaschine von ihrer Seite niederen Druckes abzudichten, sowohl hinsichtlich der Form der Dichtspalte bzw. der sie bildenden Flächen als auch hinsichtlich der Bedeutung der örtlichen und zeitlichen jeweiligen Dichtspaltposition während der Umdrehung der Dichtspalte bildenden Läufer.The improved compromise is based on the different evaluation of the different surface areas of the inner rotor when forming the sealing gap together with the outer rotor in order to seal the pressure side of the rotary piston machine from its side of low pressure, both with regard to the shape of the sealing gap or the surfaces forming it and also with regard to the meaning the local and temporal respective sealing gap position during the rotation of the rotor forming the sealing gap.

Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der abhängigen Patentansprüche und werden im folgenden anhand der Zeichnungen näher erläutert. Es zeigen:

  • Fig. 1 und 2 einen Axial- und Radialquerschnitt eines Ausführungsbeispieles einer innenachsigen Drehkolbenmaschine,
  • Fig.3a bis 31 Drehpositionen der Drehkolbenmaschine nach Fig. 1 und 2,
  • Fig. 4 bis 6 Ausführungsformen der Erfindung an einer Maschine entsprechend den Fig. 1 bis 3 und
  • Fig. 7 eine weitere Ausführungsform der Erfindung an einer anderen innenachsigen Drehkolbenmaschine.
Advantageous embodiments of the invention are the subject of the dependent claims and are explained in more detail below with reference to the drawings. Show it:
  • 1 and 2 an axial and radial cross section of an embodiment of an inner-axis rotary lobe machine,
  • 3a to 31 rotary positions of the rotary piston machine according to FIGS. 1 and 2,
  • Fig. 4 to 6 embodiments of the invention on a machine corresponding to Figs. 1 to 3 and
  • Fig. 7 shows another embodiment of the invention on another inner-axis rotary lobe machine.

Die in den Zeichnungen gezeigten Ausführungsbeispiele von Drehkolbenmaschinen entsprechend den Fig. 1 bis 6 und 7 sind sich ähnlich, da bei beiden das Drehzahlverhältnis zwischen Aussenläufer 2 und Innenläufer 3 2:3 beträgt, mit entsprechendem Verhältnis der Anzahl von Eingriffsteilen 2a, 2b, 2c am Aussenläufer und am Innenläufer 3a, 3b. Die Erfindung ist jedoch allgemein an innenachsigen Drehkolbenmaschinen anwendbar, beispielsweise auch mit einem Drehzahlverhältnis von 4:3, 5:4 u.a..The exemplary embodiments of rotary piston machines shown in the drawings corresponding to FIGS. 1 to 6 and 7 are similar, since in both the speed ratio between outer rotor 2 and inner rotor 3 is 2: 3, with a corresponding ratio of the number of engagement parts 2a, 2b, 2c on External rotor and on the inner rotor 3a, 3b. However, the invention is generally applicable to internal-axis rotary lobe machines, for example also with a speed ratio of 4: 3, 5: 4 and others.

Entsprechend dem Grundprinzip innenachsiger Drehkolbenmaschinen umschliesst der äussere Umfang 4 des Aussenläufers 2 die feststehend relativ zum Maschinengehäuse 1 angeordnete Achse 5 des Innenläufers 3, und die Achsen 5,6 beider Läufer 2,3 sind mit Abstand voneinander angeordnet. Die gegenseitige Anordnung der Läufer 2,3 bzw. ihrer Achsen 5,6 ist folglich mit derjenigen an einem Getriebe mit innenverzahntem Stirnzahnrad vergleichbar.According to the basic principle of inner-axis rotary lobe machines, the outer circumference 4 of the outer rotor 2 surrounds the axis 5 of the inner rotor 3, which is fixed relative to the machine housing 1, and the axes 5, 6 of both rotors 2, 3 are arranged at a distance from one another. The mutual arrangement of the rotors 2, 3 or their axes 5, 6 is consequently comparable to that on a gear with an internally toothed spur gear.

Um die am Umfang des Gehäuses 1 vorgesehenen Kanäle, d.h. den Einlasskanal 7 und den Auslasskanal 8 in der Maschine gegeneinander abzudichten, befinden sich beide Läufer 2,3 an mehreren Dichtstellen bzw. Dichtbereichen Di, D2, D3, D4, Ds... in dichtspaltbildender Annäherung aneinander, und entlang von zwei einander gegenüberliegenden Umfangsbereichen 10, 11 befindet sich der äussere Umfang 4 der Eingriffsteile 2a,2b,2c des Aussenläufers und/oder der äussere Umfang 12 der Eingriffsteile 3a,3b des Innenläufers 2 in dichtspaltbildender Annäherung an der Innenfläche des Maschinengehäuses 1. Diese Annäherung bzw. die Breite dieser Dichtspalte beträgt je nach Fertigungsqualität oder abhängig vom Anwendungszweck der Maschine bzw. von der Dichte des die Maschine durchströmenden Mediums in der Grössenordnung von beispielsweise 0,05 bis 0,1 mm.In order to seal the channels provided on the circumference of the housing 1, that is to say the inlet channel 7 and the outlet channel 8 in the machine, both runners 2 , 3 are located at a plurality of sealing points or sealing areas Di, D 2 , D 3 , D 4 , Ds. .. in a gap-forming approach to one another, and along two mutually opposite circumferential regions 10, 11 is the outer circumference 4 of the engagement parts 2a, 2b, 2c of the outer rotor and / or the outer circumference 12 of the engagement parts 3a, 3b of the inner rotor 2 in a gap-forming approach on the inner surface of the machine housing 1. This approximation or the width of these sealing gaps is, depending on the manufacturing quality or depending on the application of the machine or on the density of the medium flowing through the machine, in the order of magnitude of, for example, 0.05 to 0.1 mm.

Der Darstellung der Fig.1 ist zu entnehmen, dass die Umfangsflächen der Läufer 2,3 und des Gehäuses 1, die sich örtlich bzw. zeitlich verändernde Dichtspalte miteinander bilden, parallel zu den ebenfalls zueinander parallelen Achsen 5,6 der Läufer 2,3 verlaufen. Die Wellenzapfen 14,15 des Innenläufers 3 sind durch Wälzlager 16,17 an den seitlichen Gehäuseplatten 1a,1b gelagert,während der Aussenläufer 2 mit seinen nabenförmigen hohlen Achszapfen 18,19 auf Wälzlagern 20,21 an diesen Gehäuseseitenplatten 1a,1b gelagert ist, die die Wälzlager 16,17 des Innenläufers 3 umschliessen. An der Innenseite der Gehäuseseitenplatten 1a,1b befestigte stationäre Abdichtplatten 22,23 dichten die zwischen beiden Läufern 2,3 gebildeten Arbeitsräume der Maschine in axialer Richtung ab, so dass die zueinander parallelen Seitenflächen 24,25 des Innenläufers 3 sich in dichtspaltbildendem Abstand an diesen Abdichtplatten 22,23 parallel zu ihnen entlangbewegen. Obwohl es aufgrund des zahnradartigen gegenseitigen Eingriffs zwischen beiden Läufern nicht grundsätzlich erforderlich ist, stehen beide Läufer 2,3 über Zahnräder 26,27 in Antriebsverbindung, von denen eines an der Innenseite des nabenförmigen hohlen Achszapfens 19 durch eine Innenverzahnung gebildet ist. Das aussen auf dem Wellenzapfen 15 des Innenläufers 3 aufgesetzte Zahnrad 28 dient dem An- oder Abtrieb, je nachdem, ob die Maschine durch einen Gasstrom angetrieben wird oder einen solchen als Kompressor fördert.It can be seen from the illustration in FIG. 1 that the peripheral surfaces of the rotors 2, 3 and the housing 1, which form sealing gaps that change with one another in terms of location or time, run parallel to the axes 5, 6 of the rotors 2, 3, which are also parallel to one another . The shaft journals 14, 15 of the inner rotor 3 are supported by roller bearings 16, 17 on the side housing plates 1a, 1b, while the outer rotor 2 with its hub-shaped hollow axle journals 18, 19 is supported on roller bearings 20, 21 on these housing side plates 1a, 1b, which enclose the rolling bearings 16, 17 of the inner rotor 3. Stationary sealing plates 22, 23 fastened to the inside of the housing side plates 1 a, 1 b seal the working spaces of the machine formed between the two rotors 2, 3 in the axial direction, so that the mutually parallel side surfaces 24, 25 of the inner rotor 3 are formed on these sealing plates at a gap-forming distance 22.23 move parallel to them. Although it is not fundamentally necessary due to the gear-like mutual engagement between the two runners, both runners 2, 3 are in drive connection via gear wheels 26, 27, one of which is formed on the inside of the hub-shaped hollow journal 19 by an internal toothing. The gearwheel 28, which is placed on the outside of the shaft journal 15 of the inner rotor 3, is used for driving or driving, depending on whether the machine is driven by a gas flow or promotes it as a compressor.

Das Arbeitsprinzip sowie der kinematische Aufbau der in den Fig. 1 bis 3 dargestellten Maschine sind in der nichtvorveröffentlichten älteren Patentanmeldung entsprechend der DE-A-3 432 915 näher beschrieben.The working principle and the kinematic structure of the machine shown in FIGS. 1 to 3 are described in more detail in the unpublished older patent application according to DE-A-3 432 915.

In den Fig. 4 bis 7 ist die Breite der sich an den jeweiligen Dichtstellen bzw. Dichtbereichen D1 bis Ds ergebenden Dichtspalte mit örtlichem Bezug auf den Innenläufer (Fig.4, Fig. 5 und Fig.7) oder Aussenläufer (Fig.6) durch Strichlinien in starker Vergrösserung, d.h. schematisch dargestellt, indem die Strichlinien die Grösse des Innen- oder Aussenläufers abgeben, bei der sich gegenüber dem anderen Läufer kein Dichtspalt ergeben würde. Die tatsächliche Breite der Dichtspalte beträgt an den engsten fabrikationsmässig hergestellten Dichtspalten beispielsweise 0,05 mm und an den breitesten fabrikationsmässig hergestellten Dichtstellen beispielsweise 0,1 mm.4 to 7 the width of the sealing gaps resulting at the respective sealing points or sealing areas D 1 to Ds with a local reference to the inner rotor (FIGS. 4, 5 and 7) or outer rotor (FIG. 6 ) by dashed lines in large enlargement, ie schematically represented by the dashed lines the size of the inner or outer surface surrender where there would be no sealing gap with the other runner. The actual width of the sealing gaps is, for example, 0.05 mm at the narrowest sealing gaps manufactured by manufacture and, for example, 0.1 mm at the widest sealing joints manufactured by manufacture.

Erfindungsgemäss ist in jedem Fall ein Dichtspalt zwischen einer radial äusseren Umfangsfläche 12a,12b des Innenläufers 3 und einem Eingriffsteil 2a,2b,2c des Aussenläufers, wie er an den Stellen Ds, bzw. in den Fig. 3a bis 3f und Fig. 3i bis 31, auftritt, am kleinsten, wie in den Ausführungsbeispielen der Fig.4 und 5 durch die in geringerem Abstand von den Umfangsflächen 12a,12b verlaufende Strichlinie angedeutet ist, ebenso an den Umfangsflächen 12a',12b' des Ausführungsbeispieles der Fig.7. Beim Ausführungsbeispiel der Fig.6 ergibt sich der kleinste Dichtspalt an den gleichen Eingriffstellen D3 zwischen den Läufern 2,3 durch entsprechende kleinere Dimensionierung der Eingriffsteile 2a,2b,2c, wie durch die ausgezogene Konturlinie im Vergleich zu der strichlierten Konturlinie dieser Eingriffsteile angedeutet ist. An den radial inneren Eckbereichen 30 ist folglich der Abstand zwischen der theoretischen strichlierten Konturlinie und der ausgezogenen Konturlinie am kleinsten. Anstatt nur an dem Innenläufer (Fig.4,Fig.5 und Fig.7) oder nur an dem Aussenläufer (Fig.6) durch entsprechend kleinere, d.h. einen Dichtspalt berücksichtigende Dimensionierung, kann jedoch auf nicht dargestellte Weise eine entsprechende Unterdimensionierung gegenüber der theoretischen dichtspaltfreien Kontur zu je einem Teil auch an beiden Läufern 2,3 vorgesehen sein.In any case, according to the invention there is a sealing gap between a radially outer circumferential surface 12a, 12b of the inner rotor 3 and an engaging part 2a, 2b, 2c of the outer rotor, as it is at the points Ds, or in FIGS. 3a to 3f and 3i to 31 occurs, the smallest, as indicated in the exemplary embodiments in FIGS. 4 and 5 by the dashed line running at a smaller distance from the peripheral surfaces 12a, 12b, and also on the peripheral surfaces 12a ', 12b' of the exemplary embodiment in FIG. 7. In the exemplary embodiment in FIG. 6, the smallest sealing gap at the same engagement points D 3 between the runners 2, 3 results from correspondingly smaller dimensions of the engagement parts 2a, 2b, 2c, as indicated by the solid contour line in comparison to the dashed contour line of these engagement parts . The distance between the theoretical dashed contour line and the solid contour line is consequently smallest at the radially inner corner regions 30. Instead of only on the inner rotor (Fig. 4, Fig. 5 and Fig. 7) or only on the outer rotor (Fig. 6) by means of correspondingly smaller dimensions, ie taking into account a sealing gap, a corresponding undersizing compared to the theoretical can be shown in a manner not shown a seal-free contour can also be provided in part on both rotors 2, 3.

Die Auswahl kleiner Dichtspalte am äusseren Umfang des Innenläufers 3 ist durch die grössere Bedeutung einer guten Abdichtung in diesem Bereich entsprechenden den Drehpositionen der Fig. 3a bis 3f und Fig. 3i bis 31 begründet, da in diesen Drehpositionen die Nieder- und Hochdruckseite der Maschine nur über einen Dichtspalt Ds voneinander getrennt sind und aufgrund des in Umfangsrichtung kurzen Annäherungsbereiches zwischen den Flächen beider Läufer dieser Dichtspalt D3 eine verhältnismässig schlechte Dichtwirkung hat.The selection of small sealing gaps on the outer circumference of the inner rotor 3 is due to the greater importance of a good seal in this area corresponding to the rotational positions of FIGS. 3a to 3f and 3i to 31, since in these rotational positions the low and high pressure side of the machine only are separated from one another via a sealing gap Ds and, owing to the short area of approach between the surfaces of the two runners in the circumferential direction, this sealing gap D 3 has a relatively poor sealing effect.

Die im Bereich der radial inneren Umfangsflächen 32,33 des Innenläufers 3 während der Umdrehung der Läufer zwischen beiden vorkommenden Dichtspalte D4 haben zwar ebenfalls allein die Nieder- und Hochdruckseite der Maschine voneinander zu trennen, jedoch können dort zur Verringerung von Reibungsverlusten breitere Dichtspalte D4 akzeptiert werden, da in diesem Bereich die Flächen beider Läufer 2,3 angrenzend an den Dichtspalt sich in geringem Abstand voneinander befinden und somit zur Abdichtung beitragen, bzw. den Dichtspalt in Umfangsrichtung verbreitern. Grössere bzw. weitere Dichtspalte an den radial inneren Umfangsflächen 32, 33 erbringen den weiteren Vorteil einer Verringerung von Verlusten durch Quetschströmungen, insbesondere wann die Maschine für hohe Drehgeschwindigkeiten von z.B. mehr als 20 000 U/min vorgesehen ist. Fig.4 zeigt das entsprechende Ausführungsbeispiel.The sealing gaps D 4 occurring in the area of the radially inner circumferential surfaces 32, 33 of the inner rotor 3 during the rotation of the rotor also have to separate the low and high pressure sides of the machine from one another, but there can be wider sealing gaps D 4 to reduce frictional losses are accepted, since in this area the surfaces of both runners 2, 3 adjacent to the sealing gap are located at a short distance from one another and thus contribute to the sealing, or widen the sealing gap in the circumferential direction. Larger or further sealing gaps on the radially inner circumferential surfaces 32, 33 provide the further advantage of reducing losses due to squeezing currents, in particular when the machine is intended for high rotational speeds of, for example, more than 20,000 rpm. Fig. 4 shows the corresponding embodiment.

Falls die Maschine jedoch überwiegend für verhältnismässig geringe Drehgeschwindigkeiten und Gase geringer Dichte vorgesehen ist, so werden vorzugsweise auch an den genannten radial inneren Umfangsflächen 32,33 des Innenläufers engere Dichtspalte D4 vorgesehen, um eine gute Abdichtung zu erhalten, wie das Ausführungsbeispiel der Fig.5 zeigt.However, if the machine is primarily intended for relatively low rotational speeds and gases with low density, narrower sealing gaps D 4 are preferably also provided on the radially inner circumferential surfaces 32, 33 of the inner rotor in order to obtain a good seal, as the exemplary embodiment in FIG. 5 shows.

Im Bereich der zwischen den radial äusseren Umfangsflächen 12a,12b und den radial inneren Umfangsflächen 32,33 gelegenen Uebergangsflächen 34 sind die gegenüber den Innenflächen 35,36 der Eingriffteile 2a,2b,2c auftretenden Dichtspalte D bei jeder erfindungsgemässen Ausführungsform weiter als im Bereich der radial äusseren Umfangsflächen 12a,12b, so dass die dort auftretenden Reibungsverluste entsprechend gering sind. Dies ist ohne wesentliche Dichtverluste möglich, da diese Dichtspalte Di,D2 entsprechend den Darstellungen der Drehpositionen in den Fig.3a bis 31 nur auftreten, wenn die radial äusseren Umfangsflächen 12a,12b sich in dichtender Annäherung an den Umfangsbereichen 10,11 der Gehäuseinnenfläche befinden, so dass sie nicht allein die Niederdruckseite gegenüber der Hochdruckseite der Maschine abzudichten haben. Ausserdem ist an diesen Uebergangsflächen aufgrund ihres zahnflankenartigen Eingriffs mit den Innenflächen 35,36 und der entsprechend flacher in Richtung des Druckgefälles auslaufenden dichtspaltbildenden Flächen ohnehin eine bessere Dichtwirkung vorhanden.In the region of the transition surfaces 34 located between the radially outer circumferential surfaces 12a, 12b and the radially inner circumferential surfaces 32,33, the sealing gaps D which occur with respect to the inner surfaces 35,36 of the engagement parts 2a, 2b, 2c are wider in each embodiment according to the invention than in the region of the radial outer peripheral surfaces 12a, 12b, so that the friction losses occurring there are correspondingly low. This is possible without significant sealing losses, since these sealing gaps D i , D 2, in accordance with the representations of the rotational positions in FIGS. 3a to 31, only occur if the radially outer peripheral surfaces 12a, 12b are sealingly approaching the peripheral regions 10, 11 of the housing inner surface are located so that they do not have to seal only the low-pressure side from the high-pressure side of the machine. In addition, a better sealing effect is present anyway on these transition surfaces due to their tooth-flank-like engagement with the inner surfaces 35, 36 and the correspondingly flatter sealing-gap-forming surfaces tapering in the direction of the pressure gradient.

Aufgrund der vorhandenen Eingriffspositionen bei Dichtspaltbildung an den Uebergangsflächen 34 in der zuvorerwähnten Art kann die Weite der Dichtspalte Di,D2 vorteilhaft zunehmend grösser sein, entsprechend ihrem Abstand von der Achse 5 des Innenläufers, wie in Fig.5 und 6 gezeigt ist, so dass das für die entsprechenden Dichtspaltweiten am Innen- oder Aussenläufer vorzusehende Untermass radial nach aussen zunimmt.Due to the existing engagement positions when a sealing gap is formed on the transition surfaces 34 in the aforementioned manner, the width of the sealing gap Di, D 2 can advantageously be increasingly larger, corresponding to their distance from the axis 5 of the inner rotor, as shown in FIGS. 5 and 6, so that the undersize to be provided for the corresponding sealing gap widths on the inner or outer rotor increases radially outwards.

Claims (5)

1. Internally axed single-rotation machine with an external rotor and an internal rotor, which are surrounded by a common casing (1) circumferentially provided with an intake duct and an outlet duct (7, 8) and which are supported independent of each other at fixed geometric axes, whereby as a result of the reciprocal engagement of the rotors between in each case two engaging parts of the external rotor following one another in circumferential direction they form working spaces with a variable volume sealed continuously against one another by sealing gap-forming rolling and/or sliding of alternating face regions of the rotors (2, 3) on one another and in which, based on its rotation axis, the internal rotor (3) has radially outer and radially inner circumferential surfaces (12a, 12b; 32, 33), as well as transition surfaces (34) between them, characterized in that the sealing gaps (D3) between the two rotors (2, 3) are smaller on the radially outer circumferential surfaces (12a, 12b) of internal rotor (3) than on its transition surfaces (34).
2. Single-rotation machine according to claim 1, characterized in that the sealing gaps (D3) on the radially outer circumferential surfaces (12a, 12b) of the internal rotor (3) are smaller than on its radially inner circumferential surfaces (32, 33; Fig. 4).
3. Single-rotation machine according to claims 1 or 2, characterized in that the sealing gaps (D4) occurring on the radially inner circumferential surfaces (32, 33) are smaller than the sealing gaps (Ds) occurring on the transition surfaces (34) of the internal rotor (3).
4. Single-rotation machine according to one of the claims 1 to 3, characterized in that in the radially outward direction, the sealing gaps (Ds) occurring on the transition surfaces (34) have an increasing width.
5. Single-rotation machine according to one of the claims 1 to 4, characterized in that the sealing gaps (D1 to Ds) are formed on one or both rotors by a corresponding undersize compared with the kinematically produced, sealing gap-free shape of the rotors (2, 3).
EP86109613A 1985-08-31 1986-07-14 Internal-axis rotary piston machine Expired - Lifetime EP0218806B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86109613T ATE49626T1 (en) 1985-08-31 1986-07-14 INBOARD ROTARY LOBE MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3742/85A CH667492A5 (en) 1985-08-31 1985-08-31 INNER AXIS ROTARY PISTON.
CH3742/85 1985-08-31

Publications (2)

Publication Number Publication Date
EP0218806A1 EP0218806A1 (en) 1987-04-22
EP0218806B1 true EP0218806B1 (en) 1990-01-17

Family

ID=4262521

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86109613A Expired - Lifetime EP0218806B1 (en) 1985-08-31 1986-07-14 Internal-axis rotary piston machine

Country Status (10)

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US (1) US4772191A (en)
EP (1) EP0218806B1 (en)
JP (1) JPH079161B2 (en)
KR (1) KR950003057B1 (en)
AT (1) ATE49626T1 (en)
BR (1) BR8603853A (en)
CH (1) CH667492A5 (en)
DE (1) DE3668345D1 (en)
ES (1) ES2001514A6 (en)
MX (1) MX168262B (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2720788B1 (en) * 1994-06-01 1996-09-20 Barba Willy Del Reversible volumetric machine with rotary piston (s) without valve for use as engine fluid compressor and fluid pump.

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB316295A (en) * 1928-07-27 1930-05-15 Leblanc Vickers Maurice Sa Improvements in or relating to rotary compressors
US3029738A (en) * 1958-09-02 1962-04-17 Borsig Ag Control for rotary piston machines
US3275225A (en) * 1964-04-06 1966-09-27 Midland Ross Corp Fluid compressor
DE2058860C2 (en) * 1970-11-30 1983-02-10 Fürstlich Hohenzollernsche Hüttenverwaltung Laucherthal, 7480 Sigmaringen Gear pump with eccentric pinion meshing with rotary gear ring - using intermediate pressure to balance radial forces on ring and pinion
DE2456252B2 (en) * 1974-11-28 1977-06-30 Kernforschungsanlage Jülich GmbH, 517OJuIiCh SEALING DEVICE FOR A ROTARY LISTON MACHINE IN TROCHOID DESIGN
DD115184A1 (en) * 1974-12-04 1975-09-12
GB2104153B (en) * 1981-08-15 1984-08-30 Concentric Pumps Ltd Rotary positive-displacement fluid-pumps
CH664423A5 (en) * 1984-06-12 1988-02-29 Wankel Felix INNER AXIS ROTARY PISTON.

Also Published As

Publication number Publication date
BR8603853A (en) 1987-03-24
JPS6291602A (en) 1987-04-27
KR870002355A (en) 1987-03-31
ATE49626T1 (en) 1990-02-15
KR950003057B1 (en) 1995-03-30
MX168262B (en) 1993-05-14
US4772191A (en) 1988-09-20
CH667492A5 (en) 1988-10-14
EP0218806A1 (en) 1987-04-22
ES2001514A6 (en) 1988-06-01
JPH079161B2 (en) 1995-02-01
DE3668345D1 (en) 1990-02-22

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