EP0217020B1 - Internal-axis rotary piston machine - Google Patents

Internal-axis rotary piston machine Download PDF

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Publication number
EP0217020B1
EP0217020B1 EP86109614A EP86109614A EP0217020B1 EP 0217020 B1 EP0217020 B1 EP 0217020B1 EP 86109614 A EP86109614 A EP 86109614A EP 86109614 A EP86109614 A EP 86109614A EP 0217020 B1 EP0217020 B1 EP 0217020B1
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EP
European Patent Office
Prior art keywords
external rotor
side walls
radially
engagement
casting
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Expired
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EP86109614A
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German (de)
French (fr)
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EP0217020A1 (en
Inventor
Otto Kraic
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Individual
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Individual
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Priority to AT86109614T priority Critical patent/ATE42991T1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22C—FOUNDRY MOULDING
    • B22C9/00—Moulds or cores; Moulding processes
    • B22C9/10—Cores; Manufacture or installation of cores
    • B22C9/101—Permanent cores

Definitions

  • the invention relates to an internal-axis rotary piston machine, the external and internal rotors of which can be rotated about geometrical axes running through their center of gravity and parallel to one another with an integer ratio of different uniform angular velocities. which adjoins a radially outer region with surfaces which are parallel to one another or form an extension to the outside, and the engagement spaces in the axial direction are delimited by surfaces of side walls running perpendicular to the axis.
  • Machines of this type are known in numerous embodiments.
  • a machine with a speed ratio between external and internal rotor of 2: 1 is known for example from EP-A 0 087 747.
  • Machines in which this speed ratio is 3: 2 and 4: 3 are shown in the unpublished DE-3 432 915. Due to the mounting of their two rotors about axes running through their center of gravity, such machines are suitable for very high rotational speeds, so that they can be carried out with small dimensions for high throughput.
  • the pressure level that can be achieved when used as a compressor depends heavily on the precision of manufacture. Likewise, efficiency when used as a gas flow powered machine, i.e. as a driver, depends on the precision of the manufacture or on the accuracy of the mutual intervention of the runners.
  • the invention has for its object to find a machine of the type mentioned, the rotor can be executed at relatively low manufacturing costs so that there are particularly tight sealing gaps between them and the machine efficiency is particularly high accordingly.
  • This object is achieved in that a radially outer part of the side walls of the outer rotor is formed in one piece therewith and at least one body fastened to an axial end of the outer rotor forms the radially inner part of these side walls, this body with a circular shape Axis of the outer rotor concentric recess sealingly encloses a stationary sealing body which limits the radially inner space of the machine in the axial direction and through which the shaft of the inner rotor is passed.
  • the invention also relates to a method for producing a machine according to the invention and a casting mold for carrying out this method according to claims 6 and 7.
  • the surfaces delimiting the engagement spaces in the circumferential direction are already fixed to one another due to the manufacture and can be axially parallel or with precise alignment relative with the accuracy achievable in the casting process produce each other so that the inner rotor can engage in these engagement spaces with particularly narrow sealing gaps.
  • Fig. 1 illustrates the general principle of operation of an internal-axis rotary piston machine known per se. Its two rotors 2, 3 rotate about stationary geometric axes 5, 6, which are at a distance from one another, relative to the machine housing 4. The arrangement is comparable to an internally toothed gear with a ratio of the number of teeth of 3: 2 and consequently a speed ratio of 2: 3. The individual phases of the relative movement between the outer rotor 2 and the inner rotor 3 are shown in FIG. 3 of the aforementioned DE-A 3 432 915.
  • the machine housing 4 With its circular-cylindrical inner surface with a small gap distance, the machine housing 4 encloses the outer surface 8 of the sector-shaped peripheral parts 9, 10, 11, which is circular in cross-section, so that these control the inlet and outlet openings 12, 13 of the machine housing.
  • outer rotor 2 Since the outer rotor 2 has to enclose the fixed shaft journals 14, 15, which are arranged offset to its axis 5, its side parts 16, 17, which connect its peripheral parts 9, 10, 11, enclose a sufficiently large circular opening 18. This opening is closed by a sealing body 19 or 20 which is firmly connected to the machine housing 4 and through which the respective shaft journal 14, 15 is guided.
  • One of the shaft journals 14 of the inner rotor 3 carries a toothed wheel 22 which meshes with a hollow toothed wheel 23 fastened to the outer rotor 2, although such a drive connection can also be avoided due to the intermeshing engagement between the two rotors 2, 3.
  • Both runners 2, 3 are supported by ball bearings 25, 25 ', 26 for the shaft journals 14, 15 of the inner rotor 3 or by ball bearings 27, 28 for each hub part 29, 30 of the outer rotor 2, which are located on the sealing bodies 19 on both sides , 20 support directly or via a bearing block 32 connected to them.
  • the diameter of the one enclosed by the side parts 16, 17 becomes Opening 18 and thus the outside diameter of the sealing bodies 19, 20 in this area are chosen to be as small as possible and at most so large that they do not extend over the sector-shaped peripheral parts 9, 10, 11.
  • the sealing between the side parts 16, 17 rotating with the outer rotor 2 and the fixed sealing bodies 19, 20 can be carried out by simple radial seals 40, 41, and a sealing gap lying in said radial plane is created between the side surfaces of the sector-shaped peripheral parts 9, 10, 11 of the outer rotor 2 and surfaces parallel to it, delimiting the engagement spaces 33, 34, 35, of the sealing bodies 19, 20 are avoided.
  • the outer rotor 2 of a machine consists of a cast part 54 and two hub bodies 55, 56 fastened to it laterally.
  • the cast part 54 comprises the sector-shaped peripheral parts 9, 10, 11 and side parts 16, 17 connecting them, of which three pairs are consequently present .
  • Their shape is an arc of a circle, with a width in the radial direction that is smaller than the largest dimension of the sector-shaped peripheral parts 9, 10, 11 in the radial direction. Consequently, the rounded portions 50, 51, 52 of the peripheral parts 9, 10, 11 are located within a circle which is concentric with the axis 5 of the outer rotor 2 and runs along the radially inner boundary edges 58, 59, 60 of the circular-shaped side parts 16, 17.
  • the radial seal 40, 41 is not overlapped by the peripheral parts 9, 10, 11, or is located within a circle tangent to the roundings 50, 51, 52, which coincides with the opening 18 according to FIG. 1, an inner, axially engages protruding edge 62, 63 (FIG. 6) of the hub body 55, 56 or a ring 64 inserted between the casting 54 and the respective hub body 55 'in the radial direction between the side parts 16, 17 of the outer rotor 2 and the sealing body 19, 20 and thus encloses the opening 18 so that the radial seal 40, 41 is located between this edge 62, 63 of the hub body, or the inserted ring 64 (FIG. 4) and the sealing body 19, 20.
  • the configuration of the outer rotor 2 can best be seen in the illustrations in FIGS. 2, 3 and 4. 4 shows in its right part an embodiment with an inserted ring 64, which could also be provided on the opposite side of the external rotor.
  • the external rotor 2 described has the essential advantage of being inexpensive and very dimensionally producible in a casting mold, which is shown in simplified form in FIG. 5. Because the side parts 16, 17 forming part of the same cast part 54 are located radially outward than the roundings 50, 51, 52 forming the undercuts, the latter can be formed by an inner molded part 66, and the finished cast part 54 can be shown in FIG Pull off this molded part 66 in the axial direction or the molded part 66 can be pulled out of the cast part 54 in the axial direction.
  • the side wall parts 16, 17, which would prevent an axial demolding movement, are shaped by radially movable mold slides 67, 68, 69.
  • the surfaces 70 lying against one another when the mold is closed can also run flat instead of in an arc shape.
  • the inner molded part 66 has a circular circumferential collar, through which the circular arc-shaped inner boundary edge 58, 59, 60 of the side parts 16, 17 is formed, which continues into a circumferential angular groove 72, 73 (FIG. 6).
  • This angular groove 72, 73 is provided for the engagement of the edge 62, 63 of the hub body 55, 56 and extends somt past the ends of the peripheral parts 9, 10, 11, as indicated in FIG. 2 by the broken line 74.
  • the mold slides 67, 68, 69 and the inner mold part 66 thus form three mold cavities 80, 81, 82 which are connected at their ends to form the side parts 16, 17 of the outer rotor 2 .
  • the molded parts are metallic and allow a high degree of shape accuracy and surface quality of the cast part 54, so that it does not have to be machined.
  • the outer rotor 2 can have different shapes in deviation from the exemplary embodiment shown.
  • the engagement spaces 33-35 can also be delimited by planes 85-86 which run outwards or which curve outwards instead of by planar and mutually parallel surfaces 44-49, as is indicated in FIG. 3 by dashed lines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Sealing Devices (AREA)
  • Soil Working Implements (AREA)
  • Vehicle Body Suspensions (AREA)
  • Centrifugal Separators (AREA)
  • Hydraulic Motors (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The external rotor of a single-rotation machine has engagement spaces, whose boundary faces in the inward direction form a widening, which is adjacent in an outer region radial thereto to parallel surfaces or surfaces forming a widening in the outward direction. The side walls axially bounding these engagement spaces have a radially outer part, which is cast in one piece with the peripheral parts of the external rotor and an inner part radial thereto, which subsequently reduces to a circular opening the opening surrounded by the radially outer parts, so that the radial seal between side walls and a stationary sealing member surrounded by said opening is located radially within the peripheral parts of the external rotor and a sealing gap in the radial plane between the peripheral parts and the sealing member is avoided. The joining of peripheral parts and the radially outer side wall parts in one piece makes it possible to obtain the necessary high dimensional accuracy required for a good machine efficiency and this is accompanied by low manufacturing costs.

Description

Die Erfindung betrifft eine innenachsige Drehkolbenmaschine, deren Aussen- und Innenläufer um durch ihren Schwerpunkt verlaufende, zueinander parallele geometrische Achsen mit im ganzzahligen Verhältnis unterschiedlicher gleichförmiger Winkelgeschwindigkeit drehbar sind, wobei die die Eingriffsräume des Aussenläufers in Umfangsrichtung begrenzenden Flächen in Richtung nach innen eine Erweiterung bilden, die an einen dazu radial äusseren Bereich mit zueinander parallelen oder nach aussen eine Erweiterung bildenden Flächen angrenzt und wobei die Eingriffsräume in axialer Richtung durch senkrecht zur Achse verlaufende Flächen von Seitenwänden begrenzt sind.The invention relates to an internal-axis rotary piston machine, the external and internal rotors of which can be rotated about geometrical axes running through their center of gravity and parallel to one another with an integer ratio of different uniform angular velocities. which adjoins a radially outer region with surfaces which are parallel to one another or form an extension to the outside, and the engagement spaces in the axial direction are delimited by surfaces of side walls running perpendicular to the axis.

Maschinen dieser Art sind in zahlreichen Ausführungsformen bekannt. Eine Maschine mit einem Drehzahlverhältnis zwischen Aussen- und Innenläufer von 2:1 ist beispielsweise durch die EP-A 0 087 747 bekannt. Maschinen, bei denen dieses Drehzahlverhältnis 3:2 und 4:3 beträgt, sind in der nicht vorveröffentlichten DE- 3 432 915 dargestellt. Solche Maschinen sind aufgrund der Lagerung ihrer beiden Läufer um durch ihren Schwerpunkt verlaufende Achsen für sehr hohe Drehgeschwindigkeiten geeignet, so dass sie bei geringen Abmessungen für einen hohen Durchsatz ausführbar sind. Die in Anwendung als Kompressor erzielbare Druckhöhe ist jedoch stark von der Präzision der Herstellung abhängig. Ebenso ist der Wirkungsgrad bei der Anwendung als durch einen Gasstrom angetriebene Maschine, d.h. als Treiber,von der Präzision der Herstellung bzw. von der Genauigkeit des gegenseitigen Eingriffs der Läufer abhängig. Es ist deshalb bisher nicht gelungen, Maschinen der eingangsgenannten Art mit einer zufriedenstellenden Leistungsfähigkeit als Massenprodukt, d.h. mit vertretbarem Kostenaufwand herzustellen. Die Hinterschneidungen aufweisenden Eingriffsräume des Aussenläufers machten es erforderlich, den Aussenläufer aus separat hergestellten Einzelteilen zusammenzubauen, so dass auch beim Verbinden der Teile miteinander Massungenauigkeiten und ein entsprechend grosses Spiel zwischen dem Aussen- und Innenläufer unvermeidbar waren. Ohne Verwendung von Dichtleisten ist jedoch das Spiel an den Eingriffsstellen zwischen beiden Läufern, d.h. die Grösse des an diesen Stellen vorhandenen Dichtspaltes ausschlaggebend für die erzielbare Leistung der Maschine.Machines of this type are known in numerous embodiments. A machine with a speed ratio between external and internal rotor of 2: 1 is known for example from EP-A 0 087 747. Machines in which this speed ratio is 3: 2 and 4: 3 are shown in the unpublished DE-3 432 915. Due to the mounting of their two rotors about axes running through their center of gravity, such machines are suitable for very high rotational speeds, so that they can be carried out with small dimensions for high throughput. The pressure level that can be achieved when used as a compressor, however, depends heavily on the precision of manufacture. Likewise, efficiency when used as a gas flow powered machine, i.e. as a driver, depends on the precision of the manufacture or on the accuracy of the mutual intervention of the runners. It has therefore not yet been possible to use machines of the type mentioned at the outset with satisfactory performance as a mass product, i.e. to manufacture at a reasonable cost. The undercut engagement spaces of the outer rotor made it necessary to assemble the outer rotor from separately manufactured individual parts, so that even when connecting the parts to one another, dimensional inaccuracies and a correspondingly large clearance between the outer and inner rotor were inevitable. Without the use of sealing strips, however, there is play at the points of engagement between the two runners, i.e. The size of the sealing gap at these points is decisive for the achievable performance of the machine.

Der Erfindung liegt die Aufgabe zugrunde, eine Maschine der eingangsgenannten Art zu finden, deren Läufer bei verhältnismässig geringen Herstellungskosten so ausführbar sind, dass sich zwischen ihnen besonders enge Dichtspalte ergeben und der Maschinenwirkungsgrad entsprechend besonders hoch ist. Die Lösung dieser Aufgabe erfolgt dadurch, dass ein radial äusserer Teil der Seitenwände des Aussenläufers mit diesem in einem Stück geformt ist und mindestens ein an einem axialen Ende des Aussenläufers befestigter Körper den radial inneren Teil dieser Seitenwände bildet, wobei dieser Körper mit einer kreisrunden, zur Achse des Aussenläufers konzentrischen Aussparung einen stationären Abdichtkörper dichtend umschliesst, der den radial inneren Raum der Maschine in axialer Richtung begrenzt und durch den die Welle des Innenläufers hindurchgeführt ist.The invention has for its object to find a machine of the type mentioned, the rotor can be executed at relatively low manufacturing costs so that there are particularly tight sealing gaps between them and the machine efficiency is particularly high accordingly. This object is achieved in that a radially outer part of the side walls of the outer rotor is formed in one piece therewith and at least one body fastened to an axial end of the outer rotor forms the radially inner part of these side walls, this body with a circular shape Axis of the outer rotor concentric recess sealingly encloses a stationary sealing body which limits the radially inner space of the machine in the axial direction and through which the shaft of the inner rotor is passed.

Die Erfindung betrifft ausserdem ein Verfahren zur Herstellung einer erfindungsgemässen Maschine sowie eine Giessform zur Durchführung dieses Verfahrens gemäss den Patentansprüchen 6 und 7.The invention also relates to a method for producing a machine according to the invention and a casting mold for carrying out this method according to claims 6 and 7.

Dadurch, dass gemäss der Erfindung ein Teil der Seitenwände in einem Stück mit dem Aussenläufer geformt ist, sind die die Eingriffsräume in Umfangsrichtung begrenzenden Flächen bereits aufgrund der Herstellung fest zueinander fixiert und lassen sich mit der im Giessverfahren erzielbaren Genauigkeit achsparallel bzw. mit genauer Ausrichtung relativ zueinander herstellen, so dass der Innenläufer mit besonders engen Dichtspalten in diese Eingriffsräume eingreifen kann.Due to the fact that, according to the invention, part of the side walls is formed in one piece with the outer rotor, the surfaces delimiting the engagement spaces in the circumferential direction are already fixed to one another due to the manufacture and can be axially parallel or with precise alignment relative with the accuracy achievable in the casting process produce each other so that the inner rotor can engage in these engagement spaces with particularly narrow sealing gaps.

Im folgenden wird die Erfindung anhand eines in den Zeichnungen dargestellten Ausführungsbeispieles näher erläutert. Es zeigt:

  • Fig. 1 einen Radialschnitt durch eine Maschine der eingangsgenannten Art,
  • Fig. 2 eine perspektivische Darstellung eines erfindungsgemäss ausgeführten Aussenläufers einer Maschine entsprechend der Darstellung der Fig.1,
  • Fig. 3 eine hälftig radial geschnittene Endansicht des Aussenläufers nach Fig. 2,
  • Fig. 4 einen Axialschnitt durch den Aussenläufer nach Fig. 2 und 3,
  • Fig. 5 einen Radialschnitt durch die Giessform zur Herstellung des Aussenläufers und
  • Fig. 6 einen Axialschnitt durch eine erfindungsgemässe Maschine.
The invention is explained in more detail below on the basis of an exemplary embodiment shown in the drawings. It shows:
  • 1 is a radial section through a machine of the type mentioned,
  • 2 shows a perspective illustration of an external rotor of a machine designed according to the invention corresponding to the illustration in FIG.
  • 3 is a half radially sectioned end view of the outer rotor of FIG. 2,
  • 4 shows an axial section through the outer rotor according to FIGS. 2 and 3,
  • 5 shows a radial section through the casting mold for producing the external rotor and
  • 6 shows an axial section through a machine according to the invention.

Die Fig. 1 veranschaulicht das an sich bekannte allgemeine Funktionsprinzip einer innenachsigen Drehkolbenmaschine. Ihre beiden Läufer 2, 3 drehen sich um relativ zum Maschinengehäuse 4 ortsfeste geometrische Achsen 5, 6, die einen Abstand voneinander aufweisen. Die Anordnung ist vergleichbar mit einem innenverzahnten Getriebe mit einem Verhältnis der Zähnezahl von 3:2 und folglich einem Drehzahlverhältnis von 2:3. Die einzelnen Phasen der Relativbewegung zwischen dem Aussenläufer 2 und dem Innenläufer 3 sind in Fig. 3 der genannten DE-A 3 432 915 dargestellt. Das Machinengehäuse 4 umschliesst mit seiner kreiszylindrischen Innenfläche mit geringem Spaltabstand die im Querschnitt kreisbogenförmige Aussenfläche 8 der sektorförmigen Umfangsteile 9, 10, 11, so dass diese die Ein- und Austrittsöffnungen 12, 13 des Maschinengehäuses absteuern.Fig. 1 illustrates the general principle of operation of an internal-axis rotary piston machine known per se. Its two rotors 2, 3 rotate about stationary geometric axes 5, 6, which are at a distance from one another, relative to the machine housing 4. The arrangement is comparable to an internally toothed gear with a ratio of the number of teeth of 3: 2 and consequently a speed ratio of 2: 3. The individual phases of the relative movement between the outer rotor 2 and the inner rotor 3 are shown in FIG. 3 of the aforementioned DE-A 3 432 915. With its circular-cylindrical inner surface with a small gap distance, the machine housing 4 encloses the outer surface 8 of the sector-shaped peripheral parts 9, 10, 11, which is circular in cross-section, so that these control the inlet and outlet openings 12, 13 of the machine housing.

Da der Aussenläufer 2 die ortsfest gelagerten Wellenzapfen 14, 15, die versetzt zu seiner Achse 5 angeordnet sind, umschliessen muss, umschliessen seine Seitenteile 16, 17, die seine Umfangsteile 9, 10, 11 miteinander verbinden, eine hierfür ausreichend grosse kreisförmige Öffnung 18. Diese Öffnung ist durch einen mit dem Maschinengehäuse 4 fest verbundenen, Abdichtkörper 19 bzw. 20 verschlossen, durch den der jeweilige Wellenzapfen 14, 15 hindurchgeführt ist.Since the outer rotor 2 has to enclose the fixed shaft journals 14, 15, which are arranged offset to its axis 5, its side parts 16, 17, which connect its peripheral parts 9, 10, 11, enclose a sufficiently large circular opening 18. This opening is closed by a sealing body 19 or 20 which is firmly connected to the machine housing 4 and through which the respective shaft journal 14, 15 is guided.

Einer der Wellenzapfen 14 des Innenläufers 3 trägt ein Zahnrad 22, das mit einem am Aussenläufer 2 befestigten Hohlzahnrad 23 kämmt, obwohl eine solche Antriebsverbindung aufgrund des gegenseitigen kämmenden Eingriffs zwischen beiden Läufern 2, 3 auch vermeidbar ist.One of the shaft journals 14 of the inner rotor 3 carries a toothed wheel 22 which meshes with a hollow toothed wheel 23 fastened to the outer rotor 2, although such a drive connection can also be avoided due to the intermeshing engagement between the two rotors 2, 3.

Die Lagerung beider Läufer 2, 3 erfolgt durch Kugellager 25, 25', 26 für die Wellenzapfen 14, 15 des Innenläufers 3 bzw. durch Kugellager 27, 28 für je ein Nabenteil 29, 30 des Aussenläufers 2, die sich an den beidseitigen Abdichtkörpern 19, 20 unmittelbar oder über einen mit diesen verbundenen Lagerblock 32 abstützen.Both runners 2, 3 are supported by ball bearings 25, 25 ', 26 for the shaft journals 14, 15 of the inner rotor 3 or by ball bearings 27, 28 for each hub part 29, 30 of the outer rotor 2, which are located on the sealing bodies 19 on both sides , 20 support directly or via a bearing block 32 connected to them.

Für eine gute Abdichtung der Eingriffsräume 33, 34, 35 des Aussenläufers 2 gegeneinander entlang der Ebene der radial verlaufenden Seitenflächen 36, 37, entlang denen sich die Endflächen 38, 39 des Innenläufers 3 bewegen, wird der Durchmesser der von den Seitenteilen 16, 17 umschlossenen Öffnung 18 und damit der Aussendurchmesser der Abdichtkörper 19, 20 in diesem Bereich möglichst klein und maximal so gross gewählt, dass er sich nicht über die sektorförmigen Umfangsteile 9, 10, 11 erstreckt. Auf diese Weise kann die Abdichtung zwischen den mit dem Aussenläufer 2 umlaufenden Seitenteilen 16, 17 und den feststehenden Abdichtkörpern 19, 20 durch einfache Radialdichtungen 40, 41 erfolgen, und es wird ein in der genannten Radialebene liegender Dichtspalt zwischen den Seitenflächen der sektorförmigen Umfangsteile 9, 10, 11 des Aussenläufers 2 und dazu parallelen, die Eingriffsräume 33, 34, 35 begrenzenden Flächen der Abdichtkörper 19, 20 vermieden. Die Herstellung eines Aussenläufers, dessen die Eingriffsräume 33, 34, 35 in Umfangsrichtung begrenzenden Flächen 44 bis 49 eine Hinterschneidung aufweisen, die beim dargestellten Ausführungsbeispiel durch eine Abrundung 50, 51, 52 des Querschnittes der sektorförmigen Umfangsteile 9, 10, 11 in deren Scheitelbereich gebildet ist, konnte aufgrund der zuvorgenannten Gegebenheiten bisher nicht mit vertretbarem Aufwand in einem Stück erfolgen, so dass die Umfangsteile 9, 10, 11 nach separater Herstellung mit den Seitenteilen des Aussenläufers verbunden werden mussten und entsprechend grosse Toleranzen insbesondere bei der genau parallelen gegenseitigen Zuordnung dieser Umfangsteile akzeptiert werden mussten.For a good seal of the engagement spaces 33, 34, 35 of the outer rotor 2 with respect to one another along the plane of the radially extending side surfaces 36, 37, along which the end surfaces 38, 39 of the inner rotor 3 move, the diameter of the one enclosed by the side parts 16, 17 becomes Opening 18 and thus the outside diameter of the sealing bodies 19, 20 in this area are chosen to be as small as possible and at most so large that they do not extend over the sector-shaped peripheral parts 9, 10, 11. In this way, the sealing between the side parts 16, 17 rotating with the outer rotor 2 and the fixed sealing bodies 19, 20 can be carried out by simple radial seals 40, 41, and a sealing gap lying in said radial plane is created between the side surfaces of the sector-shaped peripheral parts 9, 10, 11 of the outer rotor 2 and surfaces parallel to it, delimiting the engagement spaces 33, 34, 35, of the sealing bodies 19, 20 are avoided. The manufacture of an external rotor, the surfaces 44 to 49 of which the engagement spaces 33, 34, 35 delimit in the circumferential direction have an undercut, which in the illustrated embodiment is formed by rounding 50, 51, 52 of the cross section of the sector-shaped peripheral parts 9, 10, 11 in their apex region could not be done in one piece with reasonable effort due to the aforementioned circumstances, so that the peripheral parts 9, 10, 11 had to be connected to the side parts of the outer rotor after separate production and correspondingly large tolerances, in particular in the exactly parallel mutual assignment of these peripheral parts had to be accepted.

Der Aussenläufer 2 einer erfindungsgemässen Maschine besteht aus einem Gussteil 54 und zwei seitlich an ihm befestigten Nabenkörpern 55, 56. Das Gussteil 54 umfasst die sektorförmigen Umfangsteile 9, 10, 11 und diese miteinander verbindende Seitenteile 16, 17, von denen folglich drei Paare vorhanden sind. Ihre Form ist kreisbogenförmig, mit einer Breite in radialer Richtung, die kleiner ist als die grösste Abmessung der sektorförmigen Umfangsteile 9, 10, 11 in radialer Richtung. Folglich befinden sich die Abrundungen 50, 51, 52 der Umfangsteile 9, 10, 11 innerhalb eines zur Achse 5 des Aussenläufers 2 konzentrischen Kreises, der entlang der radial inneren Begrenzungskanten 58, 59, 60 der kreisbogenförmigen Seitenteile 16, 17 verläuft. Damit die Radialdichtung 40, 41 nicht von den Umfangsteilen 9, 10, 11 überlappt wird, bzw. sich innerhalb eines die Abrundungen 50, 51, 52 tangierenden Kreises befindet, der nach Fig. 1 mit der Öffnung 18 zusammenfällt, greift ein innerer, axial abstehender Rand 62, 63 (Fig. 6) der Nabenkörper 55, 56 oder ein zwischen das Gussteil 54 und dem jeweiligen Nabenkörper 55' eingesetzter Ring 64 in radialer Richtung zwischen die Seitenteile 16, 17 des Aussenläufers 2 und den Abdichtkörper 19, 20 ein und umschliesst somit die Öffnung 18, so dass die Radialdichtung 40, 41 sich zwischen diesem Rand 62, 63 des Nabenkörpers, bzw. dem eingesetzten Ring 64 (Fig. 4) und dem Abdichtkörper 19, 20 befindet.The outer rotor 2 of a machine according to the invention consists of a cast part 54 and two hub bodies 55, 56 fastened to it laterally. The cast part 54 comprises the sector-shaped peripheral parts 9, 10, 11 and side parts 16, 17 connecting them, of which three pairs are consequently present . Their shape is an arc of a circle, with a width in the radial direction that is smaller than the largest dimension of the sector-shaped peripheral parts 9, 10, 11 in the radial direction. Consequently, the rounded portions 50, 51, 52 of the peripheral parts 9, 10, 11 are located within a circle which is concentric with the axis 5 of the outer rotor 2 and runs along the radially inner boundary edges 58, 59, 60 of the circular-shaped side parts 16, 17. So that the radial seal 40, 41 is not overlapped by the peripheral parts 9, 10, 11, or is located within a circle tangent to the roundings 50, 51, 52, which coincides with the opening 18 according to FIG. 1, an inner, axially engages protruding edge 62, 63 (FIG. 6) of the hub body 55, 56 or a ring 64 inserted between the casting 54 and the respective hub body 55 'in the radial direction between the side parts 16, 17 of the outer rotor 2 and the sealing body 19, 20 and thus encloses the opening 18 so that the radial seal 40, 41 is located between this edge 62, 63 of the hub body, or the inserted ring 64 (FIG. 4) and the sealing body 19, 20.

Die Ausgestaltung des Aussenläufers 2 ist am besten den Darstellungen der Fig. 2, 3 und 4 zu entnehmen. Die Fig. 4 zeigt in ihrem rechten Teil ein Ausführungsbeispiel mit einem eingesetzten Ring 64, der auch auf der gegenüberliegenden Seite des Aussenläufers vorgesehen sein könnte.The configuration of the outer rotor 2 can best be seen in the illustrations in FIGS. 2, 3 and 4. 4 shows in its right part an embodiment with an inserted ring 64, which could also be provided on the opposite side of the external rotor.

Der beschriebene Aussenläufer 2 hat den wesentlichen Vorteil einer kostengünstigen und sehr massgenauen Herstellbarkeit in einer Giessform, die in Fig. 5 vereinfacht dargestellt ist. Dadurch, dass sich die einen Teil des gleichen Gussteiles 54 bildenden Seitenteile 16, 17 weiter radial aussen befinden als die die Hinterschneidungen bildenden Abrundungen 50, 51, 52, können letztere durch ein inneres Formteil 66 gebildet werden, und das fertiggestellte Gussteil 54 lässt sich in axialer Richtung von diesem Formteil 66 abziehen bzw. das Formteil 66 lässt sich in axialer Richtung aus dem Gussteil 54 herausziehen. Die Seitenwandteile 16, 17, die eine axiale Entformungsbewegung verhindern würden, werden durch radialbewegliche Formschieber 67, 68, 69 geformt. Es versteht sich, dass die bei geschlossener Form aneinander liegenden Flächen 70 statt bogenförmig auch eben verlaufen können. An seinen beiden Enden hat das innere Formteil 66 einen kreisförmig umlaufenden Bund, durch den die kreisbogenförmige innere Begrenzungskante 58, 59, 60 der Seitenteile 16, 17 gebildet wird, die sich in eine umlaufende Winkelnut 72, 73 (Fig. 6) fortsetzt. Diese Winkelnut 72, 73 ist für den Eingriff des Randes 62, 63 der Nabenkörper 55, 56 vorgesehen und erstreckt sich somt hinter den Enden der Umfangsteile 9, 10, 11 vorbei, wie in Fig. 2 durch die Strichlinie 74 angedeutet ist.The external rotor 2 described has the essential advantage of being inexpensive and very dimensionally producible in a casting mold, which is shown in simplified form in FIG. 5. Because the side parts 16, 17 forming part of the same cast part 54 are located radially outward than the roundings 50, 51, 52 forming the undercuts, the latter can be formed by an inner molded part 66, and the finished cast part 54 can be shown in FIG Pull off this molded part 66 in the axial direction or the molded part 66 can be pulled out of the cast part 54 in the axial direction. The side wall parts 16, 17, which would prevent an axial demolding movement, are shaped by radially movable mold slides 67, 68, 69. It goes without saying that the surfaces 70 lying against one another when the mold is closed can also run flat instead of in an arc shape. At both ends, the inner molded part 66 has a circular circumferential collar, through which the circular arc-shaped inner boundary edge 58, 59, 60 of the side parts 16, 17 is formed, which continues into a circumferential angular groove 72, 73 (FIG. 6). This angular groove 72, 73 is provided for the engagement of the edge 62, 63 of the hub body 55, 56 and extends somt past the ends of the peripheral parts 9, 10, 11, as indicated in FIG. 2 by the broken line 74.

Zusammen mit den äusseren Formteilen 76, 77, 78 bilden die Formschieber 67, 68, 69 und das innere Formteil 66 somit drei Formhohlräume 80, 81, 82, die an ihren Enden zur Bildung der Seitenteile 16, 17, des Aussenläufers 2 miteinander verbunden sind. Die Formteile sind metallisch und ermöglichen eine hohe Formgenauigkeit und Oberflächenqualität des Gussteiles 54, so dass dieses nicht mechanisch bearbeitet werden muss.Together with the outer mold parts 76, 77, 78, the mold slides 67, 68, 69 and the inner mold part 66 thus form three mold cavities 80, 81, 82 which are connected at their ends to form the side parts 16, 17 of the outer rotor 2 . The molded parts are metallic and allow a high degree of shape accuracy and surface quality of the cast part 54, so that it does not have to be machined.

Es versteht sich, dass der Aussenläufer 2 abweichend vom dargestellten Ausführungsbeispiel verschiedene Formen aufweisen kann. Beispielsweise können die Eingriffsräume 33-35 statt durch ebene und zueinander parallel verlaufende Flächen 44-49 auch durch nach aussen auseinander laufende oder nach aussen gekrümmte Flächen 85, 86 begrenzt sein, wie in Fig. 3 durch Strichlinien angedeutet ist.It goes without saying that the outer rotor 2 can have different shapes in deviation from the exemplary embodiment shown. For example, the engagement spaces 33-35 can also be delimited by planes 85-86 which run outwards or which curve outwards instead of by planar and mutually parallel surfaces 44-49, as is indicated in FIG. 3 by dashed lines.

Es versteht sich weiterhin, dass nur solche Ausführungsformen der Maschine möglich sind, bei denen der Innenläufer 3 sich für die Montage von aussen radial nach innen in den Aussenläufer 2 einsetzen lässt.It goes without saying that only those embodiments of the machine are possible in which the inner rotor 3 can be inserted radially inward into the outer rotor 2 for mounting from the outside.

Claims (7)

1. Internally axed single-rotating machine with an external rotor and an internal rotor, which are surrounded by a common casing (4) circumferentially provided with an intake duct and an outlet duct (12, 13) and which as a result of their reciprocal engagement they form working spaces with variable volume sealed by sealing gap-forming rolling and/or sliding of alternating face regions of the rotors (2, 3), whereby the faces (44-49) bounding the engagement spaces (33-35) of the external rotor (2) in the circumferential direction form in the inward direction a widening (50-52), the engagement spaces (33-35) being axially bounded by surfaces of side walls (16, 17, 62-64) and hubs (29, 30) being provided at said side walls, characterized in that a radially outer part (16, 17) of the side walls of the external rotor (2) is shaped in one piece (54) with the engagement parts (9-11) circumferentially bounding the engagement spaces (33-35) and at least one body (62-64) fixed to the axial end of the exernal rotor (2) forms the radially inner part of said side walls (16, 17, 62-64), said body (62-64) sealingly surrounding a stationary sealing member (19, 20) with a circular recess (18) concentric to the axis (5) of the external rotor (2) and which axially defines the radially inner space of the machine and through which is passed the shaft (14, 15) of the internal rotor (3).
2. Machine according to claim 1, characterized in that the radially inner part of side walls (16, 17, 62-64) of the external rotor (2) is formed by an edge (62, 63) axially projecting from a hub body (55, 56) fixed to the external rotor (2).
3. Machine according to claim 1, characterized in that the radially inner part of the side walls (16, 17, 62-64) of the external rotor (2) is formed by a ring (64), which is held between the engagement spaces (33, 34, 35) of the external rotor (2) in circumferentially separated peripheral parts (9, 10, 11) and a body (55') laterally fixed to the external rotor (2).
4. Machine according to claim 1, characterized in that the surfaces bounding the engagement spaces (33, 35) in the circumferential direction pass into one another pairwise (45, 46; 47, 48; 49, 44) via a rounded portion (50-52) forming the widening.
5. Machine according to claim 4, characterized in that the rounded portions (50-52) pass radially outwards into planar surfaces (44-49), the radially inner parts (62-64) of the side walls (16, 17, 62-64) extending radially outwards at least up to the transition point between the rounded portions (50-52) and the planar surfaces (44-49).
6. Method for the manufacture of the machine according to claim 1, characterized by the manufacture of at least the external rotor (2) as a casting (54), the engagement spaces (33-35) of the external rotor (2) being formed by radially movable mould parts (67-69) and outer regions of an inner mould part (66) movable axially relative to casting (54) and the recess permitting the axial movement of casting (54) relative to the inner mould part (66) is reduced by fixing a body (62-64) to casting (54).
7. Casting for performing the method according to claim 6, characterized by an inner mould part (66), whose longitudinal axis coincides with the axis (5) of the casting (54) to be manufactured and which is provided on its circumference with channel-like recesses, for constructing the radially inner region of the engagement spaces (33-35) of casting (54) having the undercut (50-52) and radially movable mould sliders (67-69) for forming the radially outer region of said engagement spacers (33-35).
EP86109614A 1985-08-31 1986-07-14 Internal-axis rotary piston machine Expired EP0217020B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86109614T ATE42991T1 (en) 1985-08-31 1986-07-14 INTERNAL AXLE ROTARY ENGINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3741/85A CH667491A5 (en) 1985-08-31 1985-08-31 INNER AXIS ROTARY PISTON.
CH3741/85 1985-08-31

Publications (2)

Publication Number Publication Date
EP0217020A1 EP0217020A1 (en) 1987-04-08
EP0217020B1 true EP0217020B1 (en) 1989-05-10

Family

ID=4262498

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Application Number Title Priority Date Filing Date
EP86109614A Expired EP0217020B1 (en) 1985-08-31 1986-07-14 Internal-axis rotary piston machine

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US (1) US4850831A (en)
EP (1) EP0217020B1 (en)
JP (1) JPS6291601A (en)
AT (1) ATE42991T1 (en)
CH (1) CH667491A5 (en)
DE (1) DE3663278D1 (en)
ES (1) ES2001217A6 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2283441C1 (en) * 2005-09-30 2006-09-10 Иван Соломонович Пятов Trochold rotary machine (versions)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US724994A (en) * 1900-10-26 1903-04-07 Cooley Epicycloidal Engine Dev Company Rotary fluid-engine.
DE325849C (en) * 1917-03-03 1920-09-21 Emil Ludwig Gear pump in which a spur gear works together with an internally toothed ring gear
US1787543A (en) * 1929-01-03 1931-01-06 Nichols Thomas Winter Rotary compressor
US2053919A (en) * 1932-07-30 1936-09-08 Gulf Research Development Co Rotary pump
US2539044A (en) * 1945-08-27 1951-01-23 Gulf Research Development Co Fluid separation apparatus
US2458958A (en) * 1947-04-30 1949-01-11 Gulf Research Development Co Internal gear pump and compressor
FR1504705A (en) * 1966-10-24 1967-12-08 Volumetric system with a pair of conjugated gears
CH664193A5 (en) * 1982-03-03 1988-02-15 Wankel Felix EXHAUST-ROTATED PISTON LOADER.

Also Published As

Publication number Publication date
ATE42991T1 (en) 1989-05-15
CH667491A5 (en) 1988-10-14
DE3663278D1 (en) 1989-06-15
ES2001217A6 (en) 1988-05-01
JPS6291601A (en) 1987-04-27
EP0217020A1 (en) 1987-04-08
US4850831A (en) 1989-07-25

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