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EP0137421B1 - External axis rotary piston machine - Google Patents

External axis rotary piston machine Download PDF

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Publication number
EP0137421B1
EP0137421B1 EP84111533A EP84111533A EP0137421B1 EP 0137421 B1 EP0137421 B1 EP 0137421B1 EP 84111533 A EP84111533 A EP 84111533A EP 84111533 A EP84111533 A EP 84111533A EP 0137421 B1 EP0137421 B1 EP 0137421B1
Authority
EP
European Patent Office
Prior art keywords
piston
rotor
opening
cavity
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP84111533A
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German (de)
French (fr)
Other versions
EP0137421A3 (en
EP0137421A2 (en
Inventor
Felix Dr. H. C. Wankel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to AT84111533T priority Critical patent/ATE35020T1/en
Publication of EP0137421A2 publication Critical patent/EP0137421A2/en
Publication of EP0137421A3 publication Critical patent/EP0137421A3/xx
Application granted granted Critical
Publication of EP0137421B1 publication Critical patent/EP0137421B1/en
Expired legal-status Critical Current

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Classifications

    • 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
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • the invention relates to an external-axis rotary piston machine with the features of the preamble of claim 1.
  • a rotary piston machine of this type is known from EP-A-63 240 by the same applicant. It has a cavity in the shut-off rotor which is considerably larger than is required for the engagement of a piston of the piston rotor. This has the advantage that when the piston enters the cavity there are no squeezing flows or compressions leading to energy losses.
  • the enlarged cavity in the shut-off rotor can result in a small, though small, portion of compressed gas getting through the cavity back to the low-pressure side of the machine during the movement of the piston.
  • the circumferential surface of the piston therefore rolls on a central part of the shut-off rotor in order to form a seal against such overflow.
  • the provision of this middle part leads to a comparatively great design effort, and moreover the movement of the piston against this middle part leads locally, albeit slightly, to squeezing currents or compressions, which contribute to energy losses and noise.
  • the object of the invention is to enable the piston to pass through a cavity of the shut-off rotor to a large extent to avoid loss flows and noise, without this cavity forming a harmful space. H. an undesirable overflow from the high-pressure to the low-pressure side of the machine enables the machine to be highly efficient with low noise. This object is achieved on the basis of the features of the characterizing part of patent claim 1.
  • the invention thus shows for the first time for external-axis rotary piston machines with a piston rotor and a shut-off rotor, how a piston can remain in constant sealing contact with edge regions of the receiving opening of the cavity during its passage through a cavity of the shut-off rotor, so that a harmful space via the gas from the Pressure on the suction side can be almost completely avoided.
  • a radial displacement of an engaging edge from the circular cylindrical circumference of a shut-off rotor inwards is known per se from other types of machines.
  • the edges of the receiving opening are rounded, so that the contact with the side surfaces of the pistons takes place radially inward.
  • the boundary edges of an arcuate, flat recess in the shut-off rotor are beveled in order to enable engagement with a piston designed as a circular body .
  • the housing 1 encloses the piston rotor 2 and the shut-off rotor 3, which are mounted on the two axial ends of the housing in a manner which is not shown, but are usual, and which are in drive connection with one another in a speed ratio of 1: 2 via two gearwheels.
  • the runners 2, 3 rotate in the opposite direction, as indicated by arrows.
  • the gas to be compressed is sucked in by the movement of the pistons 4, 5 along the inner wall 6 of the housing through the housing connector 7.
  • the housing connector 7 is arranged directly adjacent to the housing part 8 sealingly enclosing the shut-off rotor 3 and opens in an approximately tangential direction into the circular-cylindrical working space 9 through which the pistons 4, 5 pass.
  • This working space is delimited on the inside by a hollow shaft 10 of the piston rotor 2. on the circumference of the pistons 4, 5 are attached.
  • the pistons can also be fastened to an outer hollow cylindrical rotor part 11, which firmly encloses an inner hollow shaft 12.
  • the hollow shaft 10 encloses a non-rotating hollow cylindrical control sleeve 13, which has an opening 14 in its wall, which extends over an arc angle. Openings 15, 16 are also respectively provided in the hollow shaft 12 in the direction of rotation in front of the pistons 4, 5. While these openings 15, 16 of the hollow shaft run through the opening 14 by rotating the rotor 2, the gas compressed in the annular space 9 can flow inward into the outflow channel 17 enclosed by the control sleeve 13.
  • the outflow opening 14 in the control sleeve 13, like the intake duct 7, is arranged as close as possible to the shut-off rotor 3 or the sealing area 18 between the two rotors 2, 3, in order to make the pistons 4, 5 one as possible with each revolution to achieve a high compression ratio.
  • the angular position of the outflow opening 14 can be changed to control the performance of the machine.
  • the opening 14 closes as shown in FIG. 3 shortly after the outer peripheral surface 19 of the piston 5 or 4, which moves along the inner wall 6 of the housing, has left the edge 20 of the annular working space 9.
  • the trailing boundary surface 21 of the opening 16 undercuts the piston 5 in the hollow shaft of the piston rotor.
  • the pistons 4, 5 begin to compress some gas into the cavity 22 of the shut-off rotor 3 until the trailing edge region 23 of the receiving opening 24 of the shut-off rotor approaches in a sealing manner or contact with the piston 5.
  • the gas compressed into the cavity 22 of the shut-off rotor during this short rotation angle of the piston runner returns to the suction side of the machine and thus reduces the efficiency of the machine.
  • this angle of rotation is reduced to a minimum, since the trailing edge region 23 of the opening 24 approaches the piston 5 much earlier than is possible according to known construction principles.
  • the drawing shows that the trailing boundary edge 25 of the receiving opening 24 of the shut-off rotor is offset radially inward, while the leading boundary edge 26 of the receiving opening 24 is located on the outer circumference of the shut-off rotor. From this trailing edge 25 of the shut-off rotor, which is offset radially inward, the edge region of the receiving opening 24 runs outward in an arc shape and merges continuously into the peripheral surface of the shut-off rotor.
  • the leading or first edge 26 on the circumference of the shut-off rotor should move along the leading piston surface 28 and the trailing, radially inwardly offset boundary edge 25 of the receiving opening 24 should move along a radially outer part 29 of the trailing piston surface, while the arcuate If the edge region 23 of the receiving opening 24 is to roll on a radially inner part of the trailing piston surface, the cross-sectional shape of the pistons 5, 4 is geometrically determined. The cross section of the pistons 5, 4 is thus approximately S-shaped.
  • the trailing or second edge of the shut-off rotor grazes along the convex surface part 29, as shown in FIGS. 4 and 5, and then, in accordance with the representations of FIGS.
  • the arcuate edge region 23 rolls on the concave surface part of the trailing piston surface.
  • the circumferential width of the pistons 4, 5 determines the size of the receiving opening 24 in the shut-off valve. This width has a certain dimension in order to obtain a sufficient seal between the circumferential surface of the pistons and the inner surface 6 of the housing 1.
  • sealing strips can be attached to the circumference of the pistons, preferably according to the principle known from DE-OS 3 005 694.
  • the gate valve can consist of a thin-walled sleeve.
  • the part of the shut-off rotor adjoining the leading opening edge 26 and the trailing arc-shaped edge region is solid and, for example, as a separately produced strip (31, 32) on the wall of the shut-off rotor attached.
  • This separate production of strips thus delimiting the receiving opening 24 facilitates the precise production of the surface contour of the edges 25 and 26 and of the convexly curved region 23 adjoining the edge 25.
  • the edges 25, 26 can, as shown in FIGS. be relatively sharp, but also be designed with a rounded cross-section.
  • FIGS. 8 and 9 show two exemplary embodiments with measures to avoid, albeit slight, squeezing currents which can occur when the convex edge region 23 rolls according to the exemplary embodiment in FIGS. 1 to 7 up to the peripheral surface 33 of the shaft of the piston rotor.
  • the convexly curved region 34 which rolls against the limiting edge 25 and rolls on the piston 5, is substantially reduced for this purpose by providing a recess 36 between this region 34 and the peripheral surface 35 of the shut-off rotor.
  • a cutout 36 instead of a cutout 36, a plurality of smaller cutouts one behind the other also in the circumferential direction of the shut-off rotor can be provided.
  • the exemplary embodiment according to FIG. 9 shows a recess 37 in the piston region which adjoins the outer convex surface part 29 of the piston 5 and merges into the peripheral surface 33 of the shaft of the piston rotor and which likewise prevents a squeezing flow which leads to losses.
  • this cutout 37 can also be replaced by a plurality of smaller cutouts.
  • the cutouts 36, 37 can also be arranged in large numbers next to one another in the axial direction, so that they are separated from one another by web parts in a manner not shown. These web parts act to weaken the cross section z. B. counter in the root region of the piston 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sealing Devices (AREA)
  • Hydraulic Motors (AREA)
  • Toys (AREA)
  • Reciprocating Pumps (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Flexible Shafts (AREA)

Abstract

An external shaft rotary piston machine wherein pistons of a piston rotor run in engagement with a cavity of a circular cylindrical sealing rotor during a particular relative rotational position of the rotors, the cavity being substantially larger than necessary for passage of the pistons in order to avoid flow losses due to seal wedging flow and compression. In order to avoid overflow from the high pressure side to the low pressure side of the machine through the sealing rotor while the pistons move in the sealing rotor through the space defined by the cavity, a sealing effect is created by a leading edge and a trailing edge portion of the opening of the cavity of the sealing rotor moving along a leading and a trailing side surface of the pistons. This is effected kinematically due to the fact that the trailing edge of the cavity opening is displaced radially inwardly and that an edge portion extends from the trailing edge convexly relative to the peripheral surface of the sealing rotor.

Description

Die Erfindung betrifft eine aussenachsige Rotationskolbenmaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to an external-axis rotary piston machine with the features of the preamble of claim 1.

Eine Rotationskolbenmaschine dieser Art ist durch die EP-A-63 240 des gleichen Anmelders bekannt. Sie hat im Absperrläufer einen Hohlraum, der wesentlich grösser ist als für den Eingriff eines Kolbens des Kolbenläufers erforderlich ist. Dies bringt den Vorteil mit sich, dass beim Eintritt des Kolbens im Hohlraum keine zu Energieverlusten führenden Quetschströmungen bzw. Kompressionen auftreten. Der vergrösserte Hohlraum im Absperrläufer kann jedoch dazu führen, dass ein wenn auch geringer Teil von komprimiertem Gas während der Bewegung des Kolbens durch den Hohlraum hindurch zurück zur Niederdruckseite der Maschine gelangt. Beim Ausführungsbeispiel der Figuren 20a bis 20e der EP-A 63 240 wälzt sich deshalb die Umfangsfläche des Kolbens an einem Mittelteil des Absperrläufers ab, um gegen ein solches Überströmen eine Abdichtung zu bilden. Das Vorsehen dieses Mittelteils führt jedoch zu einem verhältnismässig grossen konstruktiven Aufwand, und ausserdem führt die Bewegung des Kolbens gegen dieses Mittelteil örtlich zu, wenn auch geringen, Quetschströmungen oder Kompressionen, die zu Energieverlusten und zu einer Geräuschentwicklung beitragen.A rotary piston machine of this type is known from EP-A-63 240 by the same applicant. It has a cavity in the shut-off rotor which is considerably larger than is required for the engagement of a piston of the piston rotor. This has the advantage that when the piston enters the cavity there are no squeezing flows or compressions leading to energy losses. However, the enlarged cavity in the shut-off rotor can result in a small, though small, portion of compressed gas getting through the cavity back to the low-pressure side of the machine during the movement of the piston. In the embodiment of FIGS. 20a to 20e of EP-A 63 240, the circumferential surface of the piston therefore rolls on a central part of the shut-off rotor in order to form a seal against such overflow. However, the provision of this middle part leads to a comparatively great design effort, and moreover the movement of the piston against this middle part leads locally, albeit slightly, to squeezing currents or compressions, which contribute to energy losses and noise.

Der Erfindung liegt die Aufgabe zugrunde, einen weitgehendst Verlustströmungen und Geräuschentwicklungen vermeidenden Durchlauf des Kolbens durch einen Hohlraum des Absperrläufers zu ermöglichen, ohne dass dieser Hohlraum einen schädlichen Raum bildet, d. h. ein unerwünschtes Überströmen von der Hochdruck- zur Niederdruckseite der Maschine ermöglicht, so dass die Maschine bei geringer Geräuschentwicklung einen hohen Wirkungsgrad aufweist. Die Lösung dieser Aufgabe erfolgt aufgrund der Merkmale des kennzeichnenden Teiles des Patentanspruchs 1.The object of the invention is to enable the piston to pass through a cavity of the shut-off rotor to a large extent to avoid loss flows and noise, without this cavity forming a harmful space. H. an undesirable overflow from the high-pressure to the low-pressure side of the machine enables the machine to be highly efficient with low noise. This object is achieved on the basis of the features of the characterizing part of patent claim 1.

Die Erfindung zeigt somit erstmalig für aussenachsige Rotationskolbenmaschinen mit einem Kolbenläufer und einem Absperrläufer, wie ein Kolben während seines Durchlaufes durch einen Hohlraum des Absperrläufers in ständigem dichtendem Kontakt mit Randbereichen der Aufnahmeöffnung des Hohlraumes bleiben kann, so dass ein schädlicher Raum, über den Gas von der Druckauf die Saugseite gelangen kann, nahezu vollständig vermieden wird.The invention thus shows for the first time for external-axis rotary piston machines with a piston rotor and a shut-off rotor, how a piston can remain in constant sealing contact with edge regions of the receiving opening of the cavity during its passage through a cavity of the shut-off rotor, so that a harmful space via the gas from the Pressure on the suction side can be almost completely avoided.

Eine radiale Versetzung einer Eingriffskante vom kreiszylindrischen Umfang eines Absperrläufers nach innen, ist an sich durch andersartige Maschinen bekannt. Bei der innenachsigen Maschine gemäss der EP-A-88 288 mit kinematisch exaktem Eingriff der Kolben in die Aufnahmeöffnung des Absperrläufers sind die Kanten der Aufnahmeöffnung abgerundet, so dass der Kontakt mit den Seitenflächen der Kolben radial nach innen versetzt erfolgt. Bei der Maschine gemäss der GB-A-958 489 sind die Begrenzungskanten einer kreisbogenförmigen, flachen Ausnehmung des Absperrläufers abgeschrägt, um den Eingriff mit einem als Kreiskörper ausgeführten Kolben zu ermöglichen Daraus resultiert, ebenfalls zu anderem Zweck, eine radial vom Umfang nach innen versetzte Kante.A radial displacement of an engaging edge from the circular cylindrical circumference of a shut-off rotor inwards is known per se from other types of machines. In the case of the internal-axis machine according to EP-A-88 288 with kinematically exact engagement of the pistons in the receiving opening of the shut-off rotor, the edges of the receiving opening are rounded, so that the contact with the side surfaces of the pistons takes place radially inward. In the machine according to GB-A-958 489, the boundary edges of an arcuate, flat recess in the shut-off rotor are beveled in order to enable engagement with a piston designed as a circular body .

Im folgenden werden zur näheren Erläuterung der Erfindung Ausführungsbeispiele näher beschrieben. Es zeigt:

  • Fig. 1 bis 7 im Querschnitt senkrecht zu den Läuferachsen, mehrere aufeinanderfolgende Drehpositionen einer als Kompressor ausgeführten erfindungsgemässen Rotationskolbenmaschine,
  • Fig. 8 vergrössert dargestellt den Eingriffsbereich zwischen nachlaufendem Randbereich des Absperrläufers und einem Kolben bei einem weiteren Ausführungsbeispiel, und
  • Fig. 9 eine Darstellung entsprechend Fig. 8 einer dritten dargestellten Ausführungsform.
Exemplary embodiments are described in more detail below for a more detailed explanation of the invention. It shows:
  • 1 to 7 in cross section perpendicular to the rotor axes, several successive rotational positions of a rotary piston machine according to the invention designed as a compressor,
  • 8 shows an enlarged view of the engagement area between the trailing edge area of the shut-off rotor and a piston in a further exemplary embodiment, and
  • Fig. 9 is an illustration corresponding to Fig. 8 of a third embodiment shown.

Das Gehäuse 1 umschliesst den Kolbenläufer 2 und den Absperrläufer 3, die auf nicht dargestellte, jedoch übliche Weise an den beiden axialen Enden des Gehäuses gelagert sind und im Drehzahlverältnis von 1 : 2 über zwei Zahnräder miteinander in Antriebsverbindung stehen. Die Läufer 2, 3 drehen sich in entgegengesetzter Richtung, wie durch Pfeile angedeutet ist. Das zu komprimierende Gas wird durch die Bewegung der Kolben 4, 5 entlang der Innenwand 6 des Gehäuses durch den Gehäusestutzen 7 angesaugt.The housing 1 encloses the piston rotor 2 and the shut-off rotor 3, which are mounted on the two axial ends of the housing in a manner which is not shown, but are usual, and which are in drive connection with one another in a speed ratio of 1: 2 via two gearwheels. The runners 2, 3 rotate in the opposite direction, as indicated by arrows. The gas to be compressed is sucked in by the movement of the pistons 4, 5 along the inner wall 6 of the housing through the housing connector 7.

Der Gehäusestutzen 7 ist unmittelbar angrenzend an den den Absperrläufer 3 dichtend umschliessenden Gehäuseteil 8 angeordnet und mündet in angenähert tangentialer Richtung in den kreiszylindrischen, von den Kolben 4, 5 durchlaufenen Arbeitsraum 9. Dieser Arbeitsraum ist nach innen durch eine Hohlwelle 10 des Kolbenläufers 2 begrenzt, an deren Umfang die Kolben 4, 5 befestigt sind. Die Kolben können auch, wie dargestellt, an einem äusseren hohlzylindrischen Läuferteil 11 befestigt sein, das eine innere Hohlwelle 12 fest umschliesst.The housing connector 7 is arranged directly adjacent to the housing part 8 sealingly enclosing the shut-off rotor 3 and opens in an approximately tangential direction into the circular-cylindrical working space 9 through which the pistons 4, 5 pass. This working space is delimited on the inside by a hollow shaft 10 of the piston rotor 2. on the circumference of the pistons 4, 5 are attached. As shown, the pistons can also be fastened to an outer hollow cylindrical rotor part 11, which firmly encloses an inner hollow shaft 12.

Die Hohlwelle 10 umschliesst eine sich nicht mitdrehende hohlzylindriscne Steuerhülse 13, die in ihrer Wand eine Öffnung 14 aufweist, die sich über einen Bogenwinkel erstreckt. In der Hohlwelle 12 sind in Drehrichtung vor den Kolben 4, 5 ebenfalls jeweils Öffnungen 15, 16 vorhanden. Während diese Öffnungen 15, 16 der Hohlwelle durch Drehung des Läufers 2 über die Öffnung 14 hinweglaufen, kann das in dem Ringraum 9 komprimierte Gas nach innen in den von der Steuerhülse 13 umschlossenen Abströmkanal 17 abströmen. Die Abströmöffnung 14 in der Steuerhülse 13 ist ebenso wie der Ansaugkanal 7 möglichst nahe zu dem Absperrläufer 3 oder den Dichtbereich 18 zwischen beiden Läufern 2, 3 angeordnet, um bei jedem Umlauf der Kolben 4, 5 ein möglichst hohes Kompressionsverhältnis zu erzielen. Durch eine Drehbewegung der Steuerhülse 13 kann die Winkelposition der Abströmöffnung 14 zur Steuerung der Leistung der Maschine verändert werden. Für eine optimale Leistung schliesst sich die Öffnung 14 entsprechend der Darstellung in Figur 3, kurz nachdem die äussere, an der Innenwand 6 des Gehäuses sich entlang bewegende Umfangsfläche 19 des Kolbens 5 oder 4 die Kante 20 des ringförmigen Arbeitsraumes 9 verlassen hat. Um dabei die Öffnungen 14 möglichst spät schliessen zu können, hinterschneidet die nachlaufende Begrenzungsfläche 21 der Öffnung 16 in der Hohlwelle des Kolbenläufers den Kolben 5.The hollow shaft 10 encloses a non-rotating hollow cylindrical control sleeve 13, which has an opening 14 in its wall, which extends over an arc angle. Openings 15, 16 are also respectively provided in the hollow shaft 12 in the direction of rotation in front of the pistons 4, 5. While these openings 15, 16 of the hollow shaft run through the opening 14 by rotating the rotor 2, the gas compressed in the annular space 9 can flow inward into the outflow channel 17 enclosed by the control sleeve 13. The outflow opening 14 in the control sleeve 13, like the intake duct 7, is arranged as close as possible to the shut-off rotor 3 or the sealing area 18 between the two rotors 2, 3, in order to make the pistons 4, 5 one as possible with each revolution to achieve a high compression ratio. By rotating the control sleeve 13, the angular position of the outflow opening 14 can be changed to control the performance of the machine. For optimum performance, the opening 14 closes as shown in FIG. 3 shortly after the outer peripheral surface 19 of the piston 5 or 4, which moves along the inner wall 6 of the housing, has left the edge 20 of the annular working space 9. In order to be able to close the openings 14 as late as possible, the trailing boundary surface 21 of the opening 16 undercuts the piston 5 in the hollow shaft of the piston rotor.

Nachdem der Kolben 5 nach Verlassen der Gehäusekante 20 den Kontakt mit der Gehäuseinnenwand 6 verloren hat, beginnen die Kolben 4, 5 etwas Gas in den Hohlraum 22 des Abperrläufers 3 hinein zu komprimieren, bis der nachlaufende Randbereich 23 der Aufnahmeöffnung 24 des Absperrläufers in dichtende Annäherung oder Kontakt mit dem Kolben 5 gelangt. Das während dieses kurzen Drehwinkels des Kolbenläufers in den Hohlraum 22 des Absperrläufers hinein komprimierte Gas gelangt zurück zur Ansaugseite der Maschine und verringert somit den Wirkungsgrad der Maschine. Aufgrund der vorliegenden Erfindung ist dieser Drehwinkel auf ein Minimum reduziert, da der nachlaufende Randbereich 23 der Öffnung 24 wesentlich früher in dichtende Annäherung an den Kolben 5 gelangt als nach bekannten Konstruktionsprinzipien möglich ist. Die zeichnerische Darstellung zeigt, dass die nachlaufende Begrenzungskante 25 der Aufnahmeöffnung 24 des Absperrläufers radial nach innen versetzt ist, während sich die vorlaufende Begrenzungskante 26 der Aufnahmeöffnung 24 am Aussenumfang des Absperrläufers befindet. Von dieser radial nach innen versetzen nachlaufenden Kante 25 des Absperrläufers aus verläuft der Randbereich der Aufnahmeöffnung 24 bogenförmig nach aussen und geht kontinuierlich in die Umfangsfläche des Absperrläufers über. Durch die Bedingung, dass sich die vorlaufende oder erste Kante 26 am Umfang des Absperrläufers entlang der vorlaufenden Kolbenfläche 28 und die nachlaufende, radial nach innen versetzte Begrenzungskante 25 der Aufnahmeöffnung 24 an einem radial äusseren Teil 29 der nachlaufenden Kolbenfläche entlang bewegen soll, während der bogenförmige Randbereich 23 der Aufnahmeöffnung 24 sich an einem radial inneren Teil der nachlaufenden Kolbenfläche abwälzen soll, ist die Querschnittsform der Kolben 5, 4 geometrisch bestimmt. Somit ist der Querschnitt der Kolben 5, 4 angenähert S-förmig gestaltet. Die nachlaufende, bzw. zweite Kante des Absperrläufers streift an dem konvexen Flächenteil 29 entlang, wie die Figuren 4 und 5 zeigen, und anschliessend wälzt sich entsprechend den Darstellungen der Figuren 6 und 7 der bogenförmige Randbereich 23 an dem konkaven Flächenteil der nachlaufenden Kolbenfläche ab. Auf diese Weise ist die Breite der Aufnahmeöffnung 24 des Absperrläufers für eine bestimmte Kolbendicke auf ein minimales Mass verringert, so dass die Maschine minimale Verluste aufgrund einer Förderung von der Hochdruck- zur Niederdruckseite aufweist. Die in Umfangsrichtung bemessene Breite der Kolben 4, 5 bestimmt die Grösse der Aufnahmeöffnung 24 in den Absperrläufer. Diese Breite hat ein bestimmtes Mass, um eine ausreichende Abdichtung zwischen der Umfangsfläche der Kolben und der Innenfläche 6 des Gehäuses 1 zu erhalten. Für eine verbesserte Abdichtung können am Umfang der Kolben Dichtleisten befestigt sein, vorzugsweise entsprechend dem durch die DE-OS 3 005 694 bekannten Prinzip.After the piston 5 has lost contact with the housing inner wall 6 after leaving the housing edge 20, the pistons 4, 5 begin to compress some gas into the cavity 22 of the shut-off rotor 3 until the trailing edge region 23 of the receiving opening 24 of the shut-off rotor approaches in a sealing manner or contact with the piston 5. The gas compressed into the cavity 22 of the shut-off rotor during this short rotation angle of the piston runner returns to the suction side of the machine and thus reduces the efficiency of the machine. On the basis of the present invention, this angle of rotation is reduced to a minimum, since the trailing edge region 23 of the opening 24 approaches the piston 5 much earlier than is possible according to known construction principles. The drawing shows that the trailing boundary edge 25 of the receiving opening 24 of the shut-off rotor is offset radially inward, while the leading boundary edge 26 of the receiving opening 24 is located on the outer circumference of the shut-off rotor. From this trailing edge 25 of the shut-off rotor, which is offset radially inward, the edge region of the receiving opening 24 runs outward in an arc shape and merges continuously into the peripheral surface of the shut-off rotor. Due to the condition that the leading or first edge 26 on the circumference of the shut-off rotor should move along the leading piston surface 28 and the trailing, radially inwardly offset boundary edge 25 of the receiving opening 24 should move along a radially outer part 29 of the trailing piston surface, while the arcuate If the edge region 23 of the receiving opening 24 is to roll on a radially inner part of the trailing piston surface, the cross-sectional shape of the pistons 5, 4 is geometrically determined. The cross section of the pistons 5, 4 is thus approximately S-shaped. The trailing or second edge of the shut-off rotor grazes along the convex surface part 29, as shown in FIGS. 4 and 5, and then, in accordance with the representations of FIGS. 6 and 7, the arcuate edge region 23 rolls on the concave surface part of the trailing piston surface. In this way, the width of the receiving opening 24 of the shut-off rotor is reduced to a minimum for a certain piston thickness, so that the machine has minimal losses due to a delivery from the high-pressure to the low-pressure side. The circumferential width of the pistons 4, 5 determines the size of the receiving opening 24 in the shut-off valve. This width has a certain dimension in order to obtain a sufficient seal between the circumferential surface of the pistons and the inner surface 6 of the housing 1. For improved sealing, sealing strips can be attached to the circumference of the pistons, preferably according to the principle known from DE-OS 3 005 694.

Aufgrund der Erfindung ist es ohne Nachteile möglich, den Hohlraum 22 des Absperrläufers so gross auszubilden, dass der Absperrläufer aus einer dünnwandigen Hülse bestehen kann. Für einen Massenausgleich des sich mit hoher und doppelter Drehzahl im Verhältnis zum Kolbenläufer drehenden Absperrläufers ist der an die vorlaufende Öffnungskante 26 und den nachlaufenden bogenförmigen Randbereich angrenzende Teil des Absperrläufers massiv ausgebildet und beispielsweise als separat hergestellte Leiste (31, 32) an der Wand des Absperrläufers befestigt. Diese separate Herstellung von somit die Aufnahmeöffnung 24 begrenzenden Leisten erleichtert die präzise Fertigung der Oberflächenkontur der Kanten 25 und 26 sowie des sich an die Kante 25 angrenzenden konvex gekrümmten Bereiches 23. Die Kanten 25, 26 können, wie in den Figuren 1 bis 8 gezeigt, relativ scharfkantig, jedoch auch mit einem abgerundeten Querschnitt ausgebildet sein.Due to the invention, it is possible without disadvantages to design the cavity 22 of the gate valve so large that the gate valve can consist of a thin-walled sleeve. For a mass balance of the shut-off rotor rotating at high and double speed in relation to the piston rotor, the part of the shut-off rotor adjoining the leading opening edge 26 and the trailing arc-shaped edge region is solid and, for example, as a separately produced strip (31, 32) on the wall of the shut-off rotor attached. This separate production of strips thus delimiting the receiving opening 24 facilitates the precise production of the surface contour of the edges 25 and 26 and of the convexly curved region 23 adjoining the edge 25. The edges 25, 26 can, as shown in FIGS. be relatively sharp, but also be designed with a rounded cross-section.

Eine geringe Abrundung der Kanten empfiehlt sich, da eine scharfkantige Kante durch Verschleiss zu Dichtverlusten führen könnte. Aufgrund der Ausführung des Absperrläufers als dünnwandige Hülse, und zusätzlich durch die Verwendung der genannten, die Öffnungskanten oder Öffnungsränder bildenden Leisten ist der Absperrläufer im Vergleich zu bekannten Konstruktionen wesentlich einfacher herstellbar.A slight rounding of the edges is recommended, since a sharp-edged edge could lead to sealing losses due to wear. Due to the design of the gate valve as a thin-walled sleeve, and additionally through the use of the above-mentioned strips that form the opening edges or edges, the gate valve is much easier to manufacture compared to known constructions.

Die Figuren 8 und 9 zeigen zwei Ausführungsbeispiele mit Massnahmen zur Vermeidung von, wenn auch geringfügigen, Quetschströmungen, die auftreten können, wenn der konvexe Randbereich 23 entsprechend dem Ausführungsbeispiel der Figuren 1 bis 7 sich bis an die Umfangsfläche 33 der Welle des Kolbenläufers abwälzt. Beim Ausführungsbeispiel nach Fig. 8 ist zu diesem Zweck der an die Begrenzungskante 25 angrezende konvex gekrümmte Bereich 34, der sich an dem Kolben 5 abwälzt, wesentlich verkleinert, indem zwischen diesem Bereich 34 und der Umfangsfläche 35 des Absperrläufers eine Aussparung 36 vorgesehen ist. Es versteht sich, dass statt einer Aussparung 36 auch in Umfangsrichtung des Absperrläufers mehrere kleinere Aussparungen hintereinander vorgesehen sein können.FIGS. 8 and 9 show two exemplary embodiments with measures to avoid, albeit slight, squeezing currents which can occur when the convex edge region 23 rolls according to the exemplary embodiment in FIGS. 1 to 7 up to the peripheral surface 33 of the shaft of the piston rotor. In the embodiment according to FIG. 8, the convexly curved region 34, which rolls against the limiting edge 25 and rolls on the piston 5, is substantially reduced for this purpose by providing a recess 36 between this region 34 and the peripheral surface 35 of the shut-off rotor. It goes without saying that instead of a cutout 36, a plurality of smaller cutouts one behind the other also in the circumferential direction of the shut-off rotor can be provided.

Das Ausführungsbeispiel nach Fig. 9 zeigt eine Aussparung 37 in dem sich radial nach innen an den äusseren konvexen Flächenteil 29 des Kolbens 5 anschliessenden und in die Umfangsfläche 33 der Welle des Kolbenläufers übergehenden Kolbenbereich, die ebenfalls eine zu Verlusten führende Quetschströmung verhindert. Es versteht sich, dass auch diese Aussparung 37 durch mehrere kleinere Aussparungen ersetzt werden kann. Weiterhin können bei beiden Ausführungsbeispieien die Aussparungen 36, 37 auch in grosser Anzahl in axialer Richtung der Läufer nebeneinander angeordnet sein, so dass sie auf nichtdargestellte Weise durch Stegteile voneinander getrennt sind. Diese Stegteile wirken einer Schwächung des Querschnittes z. B. im Wurzelbereich der Kolben 5 entgegen.The exemplary embodiment according to FIG. 9 shows a recess 37 in the piston region which adjoins the outer convex surface part 29 of the piston 5 and merges into the peripheral surface 33 of the shaft of the piston rotor and which likewise prevents a squeezing flow which leads to losses. It goes without saying that this cutout 37 can also be replaced by a plurality of smaller cutouts. Furthermore, in both exemplary embodiments, the cutouts 36, 37 can also be arranged in large numbers next to one another in the axial direction, so that they are separated from one another by web parts in a manner not shown. These web parts act to weaken the cross section z. B. counter in the root region of the piston 5.

Claims (8)

1. External axis rotary piston machine with a piston rotor (2) and a blocking rotor (3), which are surrounded by a common casing (1), the piston rotor (2) having a hollow shaft (10) surrounding a control sleeve (13) with a through-flow opening (14), so that at least one opening (16) provided in the hollow shaft covers the sleeve opening (14) during a limited rotation angle and a sealing point (18) is formed between the circular cylindrical circumferential surface of the blocking rotor (3) and the circumference of the shaft (10) of piston rotor (2) carrying at least one piston (4, 5), the blocking rotor (3) surrounds a cavity (22) having a reception opening (24) for piston (4, 5) of piston rotor (2) and which, in order to avoid compression flows, is larger at the evasion space adjacent to the leading and trailing boundary edges (26, 25) of reception (24) than would be kinematically necessary for the movement of piston (4, 5) through cavity (22) of the blocking rotor (3) and a boundary edge (26) of reception opening (24) moves sealingly along a concave surfce (28) of the piston, characterized in that the other boundary edge (25) of the reception opening (24) is radially inwardly displaced away from the circular cylindrical circumferential surface of the blocking rotor (3) and this radially inwardly displaced edge (25) moves sealingly along a radially outer, convex surface part (29) of the piston (4, 5), whilst to said other boundary edge (25) is connected a convexly curved border region (23) in the direction of the circumferential surface of the blocking rotor (3), based on the rotation axis and rolls on the surface part (29) of the piston (4, 5) of the piston rotor (2).
2. Rotary piston machine according to claim 1, characterized in that a boundary surface (21) of opening (16) in hollow shaft (10) forms an undercut with respect to the adjacent piston (4, 5).
3. Rotary piston machine according to claim 2, characterized in that the convexly curved border region (23) with varying radii of curvature passes continuously into the circumferential surface of the blocking rotor and rolls on a piston up to the circumferential surface of the piston rotor shaft.
4. Rotary piston machine according to claim 2, characterized in that between the convexly curved border region (34) and the circular cylindrical circumferential surface (35) of the blocking rotor is provided at least one cutout (36) for avoiding compression flows.
5. Rotary piston machine according to claim 2, characterized in that the convexly curved border region (23) passes continuously into the circumferential surface (35) of the blocking rotor and at least one cutout (37) is provided in the radially inner piston region connected to the outer, convex surface part (29) of a piston (5, 4).
6. Rotary piston machine according to claims 4 or 5, characterized in that there are several juxtaposed cutouts in the axial direction of the machine and are in each case separated from one another by a web part.
7. Rotary piston machine according to claim 1, characterized in that the blocking rotor issleeve- like.
8. Rotary piston machine according to claim 7, characterized in that the border regions of the reception opening (24) of blocking rotor (3) running parallel to the rotation axis are formed by ledges (31, 32) fixed to the sleeve wall.
EP84111533A 1983-10-10 1984-09-27 External axis rotary piston machine Expired EP0137421B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84111533T ATE35020T1 (en) 1983-10-10 1984-09-27 OUTBOARD ROTARY PISTON MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5516/83A CH663446A5 (en) 1983-10-10 1983-10-10 EXTERNAL ROTARY PISTON MACHINE.
CH5516/83 1983-10-10

Publications (3)

Publication Number Publication Date
EP0137421A2 EP0137421A2 (en) 1985-04-17
EP0137421A3 EP0137421A3 (en) 1985-05-15
EP0137421B1 true EP0137421B1 (en) 1988-06-08

Family

ID=4294930

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84111533A Expired EP0137421B1 (en) 1983-10-10 1984-09-27 External axis rotary piston machine

Country Status (6)

Country Link
US (1) US4626182A (en)
EP (1) EP0137421B1 (en)
JP (1) JPS60156901A (en)
AT (1) ATE35020T1 (en)
CH (1) CH663446A5 (en)
DE (1) DE3471971D1 (en)

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DE102007009291A1 (en) 2007-02-26 2008-08-28 Hagge, Stefan, Dipl.-Ing. Rotary piston engine for converting chemically bonded energy into kinetic energy, has rotor subdivided by partition axially into rotor seal segment and compression chamber segment, where partition is firmly connected with rotor housing

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US8956134B2 (en) * 2012-08-23 2015-02-17 Mallen Research Limited Fixed-vane positive displacement rotary devices
DE102013008103A1 (en) 2013-05-10 2014-11-13 Winfried Alfons Lampart Motor drives and generators with more efficient cooling system

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DE102007009291A1 (en) 2007-02-26 2008-08-28 Hagge, Stefan, Dipl.-Ing. Rotary piston engine for converting chemically bonded energy into kinetic energy, has rotor subdivided by partition axially into rotor seal segment and compression chamber segment, where partition is firmly connected with rotor housing

Also Published As

Publication number Publication date
JPS60156901A (en) 1985-08-17
EP0137421A3 (en) 1985-05-15
CH663446A5 (en) 1987-12-15
JPH0429841B2 (en) 1992-05-20
US4626182A (en) 1986-12-02
EP0137421A2 (en) 1985-04-17
ATE35020T1 (en) 1988-06-15
DE3471971D1 (en) 1988-07-14

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