EP1226338A1 - Rotary piston machine - Google Patents

Rotary piston machine

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Publication number
EP1226338A1
EP1226338A1 EP00974505A EP00974505A EP1226338A1 EP 1226338 A1 EP1226338 A1 EP 1226338A1 EP 00974505 A EP00974505 A EP 00974505A EP 00974505 A EP00974505 A EP 00974505A EP 1226338 A1 EP1226338 A1 EP 1226338A1
Authority
EP
European Patent Office
Prior art keywords
piston
annular space
machine according
housing
rotary piston
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.)
Granted
Application number
EP00974505A
Other languages
German (de)
French (fr)
Other versions
EP1226338B1 (en
Inventor
Peter Schnabl
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Individual
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Individual
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Filing date
Publication date
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Publication of EP1226338A1 publication Critical patent/EP1226338A1/en
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Publication of EP1226338B1 publication Critical patent/EP1226338B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/007—Oscillating-piston machines or engines the points of the moving element describing approximately an alternating movement in axial direction with respect to the other element

Definitions

  • the invention relates to a rotary piston machine with a housing and a piston which is rotatably arranged in a cavity of the housing and is rotatably connected to a shaft passing through the housing, wherein in the housing at least one inlet and outlet channel for supplying and discharging a working fluid or are formed from the cavity.
  • the invention has for its object to provide a rotary piston machine of the type mentioned, which is simple in construction and in which the inlet and outlet openings for the working fluid can be controlled in a simple manner.
  • the cavity has a section in the form of a cylindrical annular space coaxial with the shaft, that the piston is designed as an annular piston in the form of a cylindrical tubular section which engages in the annular space of the housing and is guided axially displaceably therein, and that the mutually facing end surfaces of the annular space and the annular piston are designed as continuous shaft surfaces with an axially parallel amplitude, the inlet and outlet openings lying within an axial region of the annular surface area, which is determined by the maximum axial distance between the troughs of the mutually facing end surfaces.
  • the rotary lobe machine according to the invention can be operated as a pump or, if the shaft surfaces of the annular space and the ring piston are formed with at least two shaft crests and wave troughs on 360 ° of the circumference, as a motor.
  • the machine will be designed so that the housing is fixed and the piston rotates with the shaft.
  • the opposite arrangement is also possible, in which the housing rotates with respect to the non-rotating piston.
  • the piston can be axially displaceably mounted on the shaft or rigidly connected to the shaft, which in turn is axially displaceably mounted in the housing.
  • the working space of the rotary piston machine is formed by the variable cavities between the sliding end surfaces of the annular space and the annular piston.
  • the respective cavity increases or decreases both due to the rotation and the axial stroke movement of the piston relative to the housing.
  • the inlet opening and the outlet opening can be arranged in the radially outer or radially inner jacket or boundary surface of the annular space in such a way that they are cyclically released through the piston wall and closed again, for example in the case of a pump to draw in and expel a working fluid or in the case of an engine to draw in a fuel mixture, compress it and then expel the combustion gases.
  • the inlet opening and the outlet opening are each arranged such that one of the openings lies in the circumferential direction and the other lies behind a wave crest of the end face of the annular space.
  • an inlet opening and an outlet opening are provided on the circumference of 360 °.
  • two inlet openings and two outlet openings per end face of the piston are preferably provided.
  • One of the end faces can be at least approximately sinusoidal.
  • the other is preferably chosen so that the most uniform axial movement of the piston is achieved during one revolution and no jerky or extreme accelerations of the piston occur in the axial direction.
  • the piston is pretensioned in the axial direction, for example by a spring, in such a way that its end surface always abuts the end surface of the associated annular space.
  • the force with which the surfaces are pressed against one another can also be regulated by the fluid pressure in the annular space.
  • a groove is formed in a lateral surface of the piston or the annular space, into which a guide element connected to the other part (annular space, piston) engages, the course of the groove in the circumferential direction corresponding to that of the waveform of the end face of the annular space.
  • At least one guide element intended for rolling contact on the other end face is rotatably mounted in one of the facing end faces of the annular space and piston.
  • annular space / annular piston arrangements of the aforementioned type are arranged coaxially to one another such that the two pistons arranged on the same shaft move together between the end faces of the two annular spaces.
  • the two pistons can be combined to form a one-piece double piston.
  • the two end faces of the cavity or of the two annular spaces combined with one another are arranged such that the maxima and minima of their wave surfaces each lie on the same generatrix of the cylindrical outer surface of the cavity. This makes it possible to ensure that the two end faces of the rotating annular piston always slide on both end faces of the cavity simultaneously when the piston rotates.
  • Fig. 1 is a schematic, perspective, partially broken
  • FIG. 2 shows a section containing the axis through the housing of the arrangement shown in FIG. 1,
  • Fig. 3 is a schematic perspective, partially broken
  • FIG. 4 shows a schematic section through the double piston arrangement according to FIG. 3 containing the axis
  • FIG. 4a shows the detail A from FIG. 4 on an enlarged scale for a modified embodiment
  • Rotary lobe machine that is operated as a pump.
  • the rotary piston machine shown in FIGS. 1 and 2 comprises a cylindrical housing 10 and an annular piston 12 in the form of a tubular section, which is located in an annular cavity 14 of the cylindrical one Housing 10 is rotatably and axially displaceably guided.
  • the piston is connected in a rotationally fixed but axially displaceable manner on the shaft 18, which passes through the housing 10, via a radial base, which is indicated by dashed lines in FIG. 1 and is designated 16, or via radial spokes.
  • Such a rotationally fixed connection which enables an axial displacement, can take place, for example, via a spline, as shown in FIG.
  • the annular space 14 has an annular end surface 20, which can have a rectilinear or curved cross section and which runs in a wave-like manner in the circumferential direction with an axially parallel wave amplitude.
  • the wavy line is approximately sinusoidal and has two wave crests or maxima 22 and two wave troughs or minima 24 in the example shown.
  • the end face or end face 26 of the annular piston 12 facing the end face 20 of the annular space 14 is also formed in a wavy line, as can be seen in FIG. 1.
  • This end surface also has two maxima or wave crests 28 and two wave troughs 30 (FIGS. 5 to 10).
  • this wavy line is designed such that the half-width of a wave crest measured in the circumferential direction, i.e. the width of the wave crest in the axial center between a wave minimum and a wave maximum is less than the half-value width of a wave trough.
  • the arrangement could also be reversed insofar as the end face 26 of the annular piston is selected to be sinusoidal and the end face 20 of the annular space 14 has narrower wave crests and wider wave troughs.
  • one of the inlet and outlet channels 32 can also be seen in the housing 10, which ends at the inner boundary wall 15 of the annular space 14 and serves for supplying or discharging a working fluid to the annular space 14, as is shown in FIGS. 5 to 16 is explained in more detail.
  • the piston 12 is tensioned against the end face 20 of the annular space 14 by a helical spring 34 arranged coaxially to the shaft 18.
  • a plate spring can also be used, which can simultaneously serve to connect the piston to the shaft in a rotationally fixed manner.
  • the axial length is shortened with the disc spring.
  • the arrangement of the end faces 20 of the annular spaces 14 is selected such that the maxima and minima of the two end faces 20 each lie on a common generatrix of the cylindrical annular spaces 14, as is also shown in FIGS. 5 to 16.
  • the end faces 26 of the double piston 12 are shaped such that the maximum or the wave crest 28 of one end face with a minimum or the wave trough 30 of the opposite end face lies jointly on a generatrix of the cylindrical annular piston 12.
  • 33 denotes a guide groove formed in the radially outer wall of the annular space 14, into which a pin 35 fastened to the piston 12 engages.
  • the guide groove follows the waveform of the end face 20 in the circumferential direction and thus controls the translational movement of the piston 12 without the end faces 20 and 26 touching.
  • this solution is only optional.
  • Figure 4a shows yet another way to reduce the sliding friction between the end surfaces 20 and 26 and thus the wear of these surfaces.
  • a roller 37 is rotatably mounted so that it can roll on the end surface 20 of the annular space 14.
  • FIGS. 5 to 10 relate to a rotary piston machine operated as a motor of the type described in FIGS. 3 and 4, but the functional explanations for this also apply to the machine according to FIGS. 1 and 2.
  • an inlet opening 36 and an outlet opening 38 are provided on a circumference of 360 ° in such a way that, based on the direction of rotation of the piston 12 pointing in the direction of arrow A, the outlet opening 38 before a wave crest 22 and the inlet opening 36 after the wave crest 22 lies.
  • the shape of the inlet opening 36 and the outlet opening 38 is usually not circular in practice, but depending on the intended use Rotary piston machine and also designed according to the type of medium flowing through in order to achieve optimal control of the medium flow.
  • Figure 5 shows the piston 12 at top dead center.
  • Four separate cavities are formed between the upper end surface 20 of the annular space 14 and the upper end surface 26 of the piston 12.
  • the cavity lying between 90 ° and 180 ° contains a maximum compressed mixture at the time of ignition.
  • the combustion gases were expelled from the cavity between 180 ° and 270 °.
  • the outlet opening 38 was closed.
  • the piston 12 rotates in the direction of arrow A, the inlet opening 36 is gradually opened, so that mixture is sucked into the cavity lying between 270 ° and 360 °.
  • the combustion chamber measured in the direction of rotation between 270 ° and 90 ° has reached its maximum expansion.
  • the outlet opening 38 is open.
  • the piston 12 is at its bottom dead center with respect to the lower end face 20 and the exhaust of the combustion gases from the combustion chamber begins. Mixture was sucked into the second cavity between 90 ° and 270 °, which is now compressed as the piston continues to rotate.
  • FIG. 6 shows the processes indicated above when the piston 12 rotates in the direction of arrow A relative to the fixed housing 10.
  • the upper inlet opening 36 is now open so that mixture can be sucked in.
  • the outlet opening 38 is closed.
  • the combustion chamber increases with the expanding combustion gases.
  • the outlet channel is fully open so that the fuel gases can be pushed out, while the inlet opening is closed, thus allowing compression in the specified range.
  • Figure 8 shows the position inverse to Figure 5, i.e. the piston 12 is in its lower dead center position with respect to the upper end face 20 of the annular space 14 and in its upper dead center position with respect to the lower end face 20 of the annular space 14.
  • the state shown in FIG. 5 then follows FIG. 10 again, in which the piston 12 has made one revolution relative to the housing and thus the four cycles, namely suction, compression, combustion and ejection of the engine.
  • FIGS. 11 to 16 show the same phases for a rotary piston machine designed as a pump. Since there are only two cycles per working stroke, namely suction and ejection, two pairs of inlet opening 36 (suction line) and outlet opening 38 (pressure line) can be provided. For the rest, the operation of the two piston / annular space arrangements is again offset by 180 ° in the same way as has already been described for the engine according to FIGS. 5 to 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Centrifugal Separators (AREA)

Abstract

The invention relates to a rotary piston machine, comprising a housing (10) and a piston (12) which is situated in a hollow area of the housing (10) in such a way that it can rotate and which is rotationally fixed to a shaft (18) that passes through the housing (10). At least one inlet channel and at least one outlet channel for guiding a working fluid in or out of the hollow area are configured in the housing (10). According to the invention, the hollow area has a section which is configured in the form of a cylindrical ring cavity that is coaxial to the shaft (18). The piston (12), as a ring piston, is configured in the form of a cylindrical tubular section which engages in the ring cavity of the housing (10) and is axially displaceably guided in said ring cavity. The end surfaces (20,26) of the ring cavity and the ring piston (12) facing away towards each other are configured as constant wavy surfaces with an axially parallel amplitude. The inlet and outlet openings are located within an axial area of the lateral surface of the ring cavity that is determined by the maximum axial interval of the wave hollows of the end surfaces (20,26) facing towards each other.

Description

Drehkolbenmaschine Rotary engine
Die Erfindung betrifft eine Drehkolbenmaschine mit einem Gehäuse und einem Kolben, der in einem Hohlraum des Gehäuses drehbar angeordnet und mit einer das Gehäuse durchsetzenden Welle drehfest verbunden ist, wobei in dem Gehäuse jeweils mindestens ein Einlaß- und Auslaßkanal zum Zuführen bzw. Abführen eines Arbeitsfluides zu bzw. aus dem Hohlraum ausgebildet sind.The invention relates to a rotary piston machine with a housing and a piston which is rotatably arranged in a cavity of the housing and is rotatably connected to a shaft passing through the housing, wherein in the housing at least one inlet and outlet channel for supplying and discharging a working fluid or are formed from the cavity.
Der Erfindung liegt die Aufgabe zugrunde, eine Drehkolbenmaschine der eingangs genannten Art anzugeben, die einfach im Aufbau ist und bei der die Einlaß- und Auslaßöffnungen für das Arbeitsfluid auf einfache Weise gesteuert werden können.The invention has for its object to provide a rotary piston machine of the type mentioned, which is simple in construction and in which the inlet and outlet openings for the working fluid can be controlled in a simple manner.
Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der Hohlraum einen Abschnitt in Form eines zur Welle koaxialen zylindrischen Ringraumes hat, daß der Kolben als Ringkolben in Form eines zylindrischen Rohrabschnittes ausgebildet ist, der in den Ringraum des Gehäuses eingreift und in diesem axial verschiebbar geführt ist, und daß die einander zugekehrten Endflächen des Ringraumes und des Ringkolbens als stetige Wellenflächen mit achsparallel gerichteter Amplitude ausgebildet sind, wobei die Einlaß- und Auslaßöffnungen innerhalb eines axialen Bereiches der Ringraummantelfläche liegen, der durch den maximalen axialen Abstand der Wellentäler der einander zugekehrten Endflächen bestimmt wird. Die erfindungsgemäße Drehkolbenmaschine kann als Pumpe oder, sofern die Wellenflächen des Ringraumes und des Ringkolbens mit mindestens zwei Wellenbergen und Wellentälern auf 360° des Umfanges ausgebildet sind, auch als Motor betrieben werden. In der Regel wird die Maschine so ausgebildet sein, daß das Gehäuse feststeht und der Kolben mit der Welle umläuft. Prinzipiell ist jedoch auch die entgegengesetzte Anordnung möglich, bei welcher sich das Gehäuse gegenüber dem nichtrotierenden Kolben dreht. Jedoch sind hier die Anschlüsse für die Zufuhr und die Abfuhr des Arbeitsfluides komplizierter. Der Kolben kann dabei auf der Welle axial verschiebbar gelagert sein oder starr mit der Welle verbunden sein, die ihrerseits axial verschiebbar in dem Gehäuse gelagert ist.This object is achieved in that the cavity has a section in the form of a cylindrical annular space coaxial with the shaft, that the piston is designed as an annular piston in the form of a cylindrical tubular section which engages in the annular space of the housing and is guided axially displaceably therein, and that the mutually facing end surfaces of the annular space and the annular piston are designed as continuous shaft surfaces with an axially parallel amplitude, the inlet and outlet openings lying within an axial region of the annular surface area, which is determined by the maximum axial distance between the troughs of the mutually facing end surfaces. The rotary lobe machine according to the invention can be operated as a pump or, if the shaft surfaces of the annular space and the ring piston are formed with at least two shaft crests and wave troughs on 360 ° of the circumference, as a motor. As a rule, the machine will be designed so that the housing is fixed and the piston rotates with the shaft. In principle, however, the opposite arrangement is also possible, in which the housing rotates with respect to the non-rotating piston. However, the connections for the supply and discharge of the working fluid are more complicated here. The piston can be axially displaceably mounted on the shaft or rigidly connected to the shaft, which in turn is axially displaceably mounted in the housing.
Bei der erfindungsgemäßen Lösung wird der Arbeitsraum der Drehkolbenmaschine durch die variablen Hohlräume zwischen den aneinander gleitenden Endflächen des Ringraumes und des Ringkolben gebildet. Dabei vergrößert oder verkleinert sich der jeweilige Hohlraum sowohl durch die Drehung als auch die axiale Hubbewegung des Kolbens gegenüber dem Gehäuse. Die Einlaßöffnung und die Auslaßöffnung können in der radial äußeren oder radial inneren Mantel- oder Begrenzungsfläche des Ringraumes so angeordnet werden, daß sie zyklisch durch die Kolbenwand freigegeben und wieder geschlossen werden, um im Falle einer Pumpe beispielsweise ein Arbeitsfluid anzusaugen und wieder auszustoßen oder im Falle eines Motors ein Treibstoffgemisch anzusaugen, zu verdichten und anschließend die Verbrennungsgase wieder auszustoßen.In the solution according to the invention, the working space of the rotary piston machine is formed by the variable cavities between the sliding end surfaces of the annular space and the annular piston. The respective cavity increases or decreases both due to the rotation and the axial stroke movement of the piston relative to the housing. The inlet opening and the outlet opening can be arranged in the radially outer or radially inner jacket or boundary surface of the annular space in such a way that they are cyclically released through the piston wall and closed again, for example in the case of a pump to draw in and expel a working fluid or in the case of an engine to draw in a fuel mixture, compress it and then expel the combustion gases.
Da der Ringkolben bezüglich seiner Drehachse rotationssymmetrisch ausgebildet ist, erhält man einen völlig ruhigen Lauf des Kolbens. Das gleiche würde für ein rotierendes Gehäuse gelten. Es treten keine wesentlichen Dichtungsprobleme auf. Bewegliche Ventile sind für das Öffnen und Schließen der Einlaß- und Auslaßöffnungen nicht erforderlich.Since the ring piston is rotationally symmetrical with respect to its axis of rotation, the piston runs completely smoothly. The same would apply to a rotating housing. There are no significant sealing problems. Movable valves are not required to open and close the inlet and outlet openings.
Vorzugsweise sind die Einlaßöffnung und die Auslaßöffnung jeweils so angeordnet, daß eine der Öffnungen in Umfangsrichtung vor und die andere hinter einem Wellenberg der Endfläche des Ringraumes liegt. Bei Ausbildung der Drehkolbenmaschine als Motor sind auf dem Umfang von 360° eine Einlaßöffnung und eine Auslaßöffnung vorgesehen. Bei Ausbildung der Drehkolbenmaschine als Pumpe sind vorzugsweise jeweils zwei Einlaßöffnungen und zwei Auslaßöffnungen pro Endfläche des Kolbens vorgesehen.Preferably, the inlet opening and the outlet opening are each arranged such that one of the openings lies in the circumferential direction and the other lies behind a wave crest of the end face of the annular space. When the rotary piston machine is designed as a motor, an inlet opening and an outlet opening are provided on the circumference of 360 °. When training the rotary lobe machine as Pump are preferably provided two inlet openings and two outlet openings per end face of the piston.
Eine der Endflächen kann zumindest annähernd sinusförmig ausgebildet sein. Die andere wird vorzugsweise so gewählt, daß eine möglichst gleichförmige axiale Bewegung des Kolbens während einer Umdrehung erreicht wird und keine ruckartigen oder extremen Beschleunigungen des Kolbens in axialer Richtung auftreten.One of the end faces can be at least approximately sinusoidal. The other is preferably chosen so that the most uniform axial movement of the piston is achieved during one revolution and no jerky or extreme accelerations of the piston occur in the axial direction.
Bei einer ersten Ausführungsform der Erfindung wird der Kolben beispielsweise durch eine Feder in axialer Richtung so vorgespannt, daß seine Endfläche stets an der Endfläche des zugehörigen Ringraumes anliegt. Die Kraft, mit der die Flächen gegeneinander gedrückt werden, kann auch durch den Fluiddruck im Ringraum geregelt werden.In a first embodiment of the invention, the piston is pretensioned in the axial direction, for example by a spring, in such a way that its end surface always abuts the end surface of the associated annular space. The force with which the surfaces are pressed against one another can also be regulated by the fluid pressure in the annular space.
Bei einer anderen Ausführungsform ist in einer Mantelfläche des Kolbens oder des Ringraumes eine Nut ausgebildet, in die ein mit dem jeweils anderen Teil (Ringraum, Kolben) verbundenes Führungselement eingreift, wobei der Verlauf der Nut in Umfangsrichtung dem der Wellenform der Endfläche des Ringraumes entspricht. Damit wird die Translationsbewegung des Kolbens und des Zylinders relativ zueinander durch die Nut gesteuert. Die Endflächen von Kolben und Ringraum müssen sich nicht berühren, sodaß der Verschleiß dieser Flächen durch das Aufeinandergleiten vermieden wird.In another embodiment, a groove is formed in a lateral surface of the piston or the annular space, into which a guide element connected to the other part (annular space, piston) engages, the course of the groove in the circumferential direction corresponding to that of the waveform of the end face of the annular space. This controls the translational movement of the piston and the cylinder relative to each other through the groove. The end faces of the piston and the annular space do not have to touch each other, so that the wear of these faces by sliding on one another is avoided.
Eine andere Lösung, den Verschleiß der Endflächen durch Gleitreibung zu vermindern, besteht darin, daß in einer der einander zugewandten Endflächen von Ringraum und Kolben mindestens ein zur rollenden Anlage an der jeweils anderen Endfläche bestimmtes Führungselement drehbar gelagert ist.Another solution to reduce the wear of the end faces due to sliding friction is that at least one guide element intended for rolling contact on the other end face is rotatably mounted in one of the facing end faces of the annular space and piston.
Bei einer weiteren Ausführungsform der Erfindung sind zwei Ringraum-/ Ringkolbenanordnungen der vorstehend genannten Art koaxial zueinander so angeordnet, daß die beiden auf derselben Welle angeordneten Kolben sich gemeinsam zwischen den Endflächen der beiden Ringräume bewegen.In a further embodiment of the invention, two annular space / annular piston arrangements of the aforementioned type are arranged coaxially to one another such that the two pistons arranged on the same shaft move together between the end faces of the two annular spaces.
Beispielsweise können die beiden Kolben zu einem einstückigen Doppelkolben vereinigt sein. Dabei sind die beiden Endflächen des Hohlraumes oder der beiden miteinander vereinigten Ringräume so zueinander angeordnet, daß die Maxima und Minima ihrer Wellenflächen jeweils auf denselben Erzeugenden der zylindrischen Mantelfläche des Hohlraumes liegen. Dadurch läßt sich sicherstellen, daß die beiden Endflächen des rotierenden Ringkolbens stets an beiden Endflächen des Hohlraums gleichzeitig gleiten, wenn der Kolben rotiert.For example, the two pistons can be combined to form a one-piece double piston. The two end faces of the cavity or of the two annular spaces combined with one another are arranged such that the maxima and minima of their wave surfaces each lie on the same generatrix of the cylindrical outer surface of the cavity. This makes it possible to ensure that the two end faces of the rotating annular piston always slide on both end faces of the cavity simultaneously when the piston rotates.
Die folgende Beschreibung erläutert in Verbindung mit den beigefügten Zeichnungen die Erfindung anhand von Ausführungsbeispielen. Es zeigen:The following description in conjunction with the accompanying drawings explains the invention using exemplary embodiments. Show it:
Fig. 1 eine schematische, perspektivische, teilweise aufgebrocheneFig. 1 is a schematic, perspective, partially broken
Darstellung einer ersten Ausführungsform einer erfindungsgemäßen Drehkolbenmaschine mit einer Kolben/Ringraumanordnung,Representation of a first embodiment of a rotary piston machine according to the invention with a piston / annulus arrangement,
Fig. 2 einen die Achse enthaltenden Schnitt durch das Gehäuse der in Figur 1 dargestellten Anordnung,2 shows a section containing the axis through the housing of the arrangement shown in FIG. 1,
Fig. 3 eine schematische perspektivische, teilweise aufgebrocheneFig. 3 is a schematic perspective, partially broken
Darstellung einer Drehkolbenmaschine mit einem Doppelkolben,Representation of a rotary piston machine with a double piston,
Fig. 4 einen schematischen, die Achse enthaltenden Schnitt durch die Doppelkolbenanordnung gemäß Figur 3,4 shows a schematic section through the double piston arrangement according to FIG. 3 containing the axis,
Fig.4a die Einzelheit A aus Fig. 4 in vergrößertem Maßstab für eine abgewandelte Ausführungsform,4a shows the detail A from FIG. 4 on an enlarged scale for a modified embodiment,
Fig. 5 bis 10 jeweils eine Abwicklungsdarstellung der aneinander gleitenden Endflächen des Gehäusehohlraumes und des Doppelkolbens einer als Motor arbeitenden Doppelkoibenmaschine gemäß den Figuren 3 und 4 und5 to 10 each show a development view of the sliding end faces of the housing cavity and the double piston of a double-piston machine working as a motor according to FIGS. 3 and 4 and
Fig. 11 bis 16 den Figuren 5 bis 10 entsprechende Darstellungen einer11 to 16 representations corresponding to FIGS. 5 to 10
Drehkolbenmaschine, die als Pumpe betrieben wird.Rotary lobe machine that is operated as a pump.
Die in den Figuren 1 und 2 dargestellte Drehkolbenmaschine umfaßt ein zylindrisches Gehäuse 10 und einen in Form eines Rohrabschnittes ausgebildeten Ringkolben 12, der in einem ringförmigen Hohlraum 14 des zylindrischen Gehäuses 10 drehbar und axial verschiebbar geführt ist. Der Kolben ist über einen radialen Boden, der in Figur 1 gestrichelt angedeutet und mit 16 bezeichnet ist oder über radiale Speichen mit einer Welle 18 drehfest, aber axial auf der Welle 18 verschiebbar verbunden, welche das Gehäuse 10 durchsetzt. Eine solche eine axiale Verschiebung ermöglichende drehfeste Verbindung kann beispielsweise über eine Keilverzahnung erfolgen, wie dies in Figur 4 dargestellt ist.The rotary piston machine shown in FIGS. 1 and 2 comprises a cylindrical housing 10 and an annular piston 12 in the form of a tubular section, which is located in an annular cavity 14 of the cylindrical one Housing 10 is rotatably and axially displaceably guided. The piston is connected in a rotationally fixed but axially displaceable manner on the shaft 18, which passes through the housing 10, via a radial base, which is indicated by dashed lines in FIG. 1 and is designated 16, or via radial spokes. Such a rotationally fixed connection, which enables an axial displacement, can take place, for example, via a spline, as shown in FIG.
Der Ringraum 14 hat eine ringförmige Endfläche 20, die einen geradlinigen oder gekrümmten Querschnitt haben kann und die in Umfangsrichtung wellenförmig verläuft mit achsparallel gerichteter Wellenamplitude. Wie man in den Figuren 5 bis 10 erkennt, ist die Wellenlinie annähernd sinusförmig und hat in dem dargestellten Beispiel zwei Wellenberge oder Maxima 22 sowie zwei Wellentäler oder Minima 24.The annular space 14 has an annular end surface 20, which can have a rectilinear or curved cross section and which runs in a wave-like manner in the circumferential direction with an axially parallel wave amplitude. As can be seen in FIGS. 5 to 10, the wavy line is approximately sinusoidal and has two wave crests or maxima 22 and two wave troughs or minima 24 in the example shown.
Die der Endfläche 20 des Ringraumes 14 zugewandte Stirn- oder Endfläche 26 des Ringkolbens 12 ist ebenfalls wellenlinienförmig ausgebildet, wie dies in der Figur 1 zu erkennen ist. Auch diese Endfläche hat zwei Maxima oder Wellenberge 28 und zwei Wellentäler 30 (Figuren 5 bis 10). Diese Wellenlinie ist jedoch so ausgebildet, daß die in Umfangsrichtung gemessene Halbwertsbreite eines Wellenberges, d.h. die Breite des Wellenberges in der axialen Mitte zwischen einem Wellenminimum und einem Wellenmaximum geringer als die Halbwertsbreite eines Wellentales ist. Die Anordnung könnte auch insofern umgekehrt gewählt sein, als die Endfläche 26 des Ringkolbens sinusförmig gewählt ist und die Endfläche 20 des Ringraumes 14 schmalere Wellenberge und breitere Wellentäler hat.The end face or end face 26 of the annular piston 12 facing the end face 20 of the annular space 14 is also formed in a wavy line, as can be seen in FIG. 1. This end surface also has two maxima or wave crests 28 and two wave troughs 30 (FIGS. 5 to 10). However, this wavy line is designed such that the half-width of a wave crest measured in the circumferential direction, i.e. the width of the wave crest in the axial center between a wave minimum and a wave maximum is less than the half-value width of a wave trough. The arrangement could also be reversed insofar as the end face 26 of the annular piston is selected to be sinusoidal and the end face 20 of the annular space 14 has narrower wave crests and wider wave troughs.
In Figur 2 ist ferner in dem Gehäuse 10 einer der Einlaß- und Auslaßkanäle 32 zu erkennen, der an der inneren Begrenzungswand 15 des Ringraumes 14 endet und zum Zuführen oder Abführen eines Arbeitsfluides zu dem Ringraum 14 dient, wie dies anhand der Figuren 5 bis 16 noch näher erläutert wird.In FIG. 2, one of the inlet and outlet channels 32 can also be seen in the housing 10, which ends at the inner boundary wall 15 of the annular space 14 and serves for supplying or discharging a working fluid to the annular space 14, as is shown in FIGS. 5 to 16 is explained in more detail.
Der Kolben 12 wird durch eine koaxial zur Welle 18 angeordnete Schraubenfeder 34 gegen die Endfläche 20 des Ringraumes 14 gespannt. Anstelle der Schraubenfeder kann auch eine Tellerfeder verwendet werden, die gleichzeitig dazu dienen kann, den Kolben drehfest mit der Welle zu verbinden. Mit der Tellerfeder wird die axiale Baulänge verkürzt. Bei der in den Figuren 3 und 4 dargestellten Ausführungsform der erfindungsgemäßen Drehkolbenmaschine sind zwei Kolben/The piston 12 is tensioned against the end face 20 of the annular space 14 by a helical spring 34 arranged coaxially to the shaft 18. Instead of the helical spring, a plate spring can also be used, which can simultaneously serve to connect the piston to the shaft in a rotationally fixed manner. The axial length is shortened with the disc spring. In the embodiment of the rotary piston machine according to the invention shown in FIGS. 3 and 4, two pistons /
Gehäuseanordnungen der in Figur 1 dargestellten Art koaxial zueinander angeordnet, wobei die Feder 34 entfällt. Die beiden Kolben sind zu einem einzigen Doppelkolben vereinigt, wobei in den Figuren gleiche Teile mit gleichen Bezugszeichen wie in den Figuren 1 und 2 bezeichnet sind.Housing arrangements of the type shown in Figure 1 arranged coaxially with each other, the spring 34 is omitted. The two pistons are combined to form a single double piston, the same parts being identified in the figures with the same reference numerals as in FIGS. 1 and 2.
Die Anordnung der Endflächen 20 der Ringräume 14 ist so gewählt, daß die Maxima und Minima der beiden Endflächen 20 jeweils auf einer gemeinsamen Erzeugenden der zylindrischen Ringräume 14 liegen, wie dies auch die Figuren 5 bis 16 zeigen.The arrangement of the end faces 20 of the annular spaces 14 is selected such that the maxima and minima of the two end faces 20 each lie on a common generatrix of the cylindrical annular spaces 14, as is also shown in FIGS. 5 to 16.
Die Endflächen 26 des Doppelkolbens 12 dagegen sind so geformt, daß das Maximum oder der Wellenberg 28 der einen Endfläche mit einem Minimum oder dem Wellental 30 der entgegengesetzten Endfläche gemeinsam auf einer Erzeugenden des zylindrischen Ringkolbens 12 liegt.The end faces 26 of the double piston 12, on the other hand, are shaped such that the maximum or the wave crest 28 of one end face with a minimum or the wave trough 30 of the opposite end face lies jointly on a generatrix of the cylindrical annular piston 12.
In Figur 3 ist mit 33 eine in der radial äußeren Wand des Ringraumes 14 ausgebildete Führungsnut bezeichnet, in die ein an dem Kolben 12 befestigter Zapfen 35 eingreift. Die Führungsnut folgt in Umfangsrichtung der Wellenform der Endfläche 20 und steuert so die Translationsbewegung des Kolbens 12, ohne daß sich die Endflächen 20 und 26 berühren. Diese Lösung ist aber nur optional.In FIG. 3, 33 denotes a guide groove formed in the radially outer wall of the annular space 14, into which a pin 35 fastened to the piston 12 engages. The guide groove follows the waveform of the end face 20 in the circumferential direction and thus controls the translational movement of the piston 12 without the end faces 20 and 26 touching. However, this solution is only optional.
Figur 4a zeigt noch eine weitere Möglichkeit, die Gleitreibung zwischen den Endflächen 20 und 26 und damit den Verschleiß dieser Flächen zu vermindern. In einer Aussparung in der Endfläche 26 des Kolbens 12 ist eine Rolle 37 drehbar gelagert, sodaß sie auf der Endfläche 20 des Ringraumes 14 rollen kann.Figure 4a shows yet another way to reduce the sliding friction between the end surfaces 20 and 26 and thus the wear of these surfaces. In a recess in the end surface 26 of the piston 12, a roller 37 is rotatably mounted so that it can roll on the end surface 20 of the annular space 14.
Die Figuren 5 bis 10 betreffen eine als Motor betriebene Drehkolbenmaschine der in den Figuren 3 und 4 beschriebenen Art, wobei die funktionalen Erläuterungen hierzu aber ebenso für die Maschine gemäß den Figuren 1 und 2 gelten. Pro Zylinder sind auf einem Umfang von 360° je eine Einlaßöffnung 36 und eine Auslaßöffnung 38 vorgesehen und zwar so, daß bezogen auf die in Richtung des Pfeiles A weisende Umlaufrichtung des Kolbens 12 die Auslaßöffnung 38 vor einem Wellenberg 22 und die Einlaßöffnung 36 nach dem Wellenberg 22 liegt. Die Form der Einlaßöffnung 36 und der Auslaßöffnung 38 ist in der Praxis meist nicht kreisförmig sondern wird je nach Verwendungszweck der Drehkolbenmaschine und auch nach Art des durchströmenden Mediums gestaltet, um eine optimale Steuerung des Mediumdurchflusses zu erreichen.FIGS. 5 to 10 relate to a rotary piston machine operated as a motor of the type described in FIGS. 3 and 4, but the functional explanations for this also apply to the machine according to FIGS. 1 and 2. For each cylinder, an inlet opening 36 and an outlet opening 38 are provided on a circumference of 360 ° in such a way that, based on the direction of rotation of the piston 12 pointing in the direction of arrow A, the outlet opening 38 before a wave crest 22 and the inlet opening 36 after the wave crest 22 lies. The shape of the inlet opening 36 and the outlet opening 38 is usually not circular in practice, but depending on the intended use Rotary piston machine and also designed according to the type of medium flowing through in order to achieve optimal control of the medium flow.
Figur 5 zeigt den Kolben 12 im oberen Totpunkt. Dabei sind zwischen der oberen Endfläche 20 des Ringraumes 14 und der oberen Endfläche 26 des Kolbens 12 vier voneinander getrennte Hohlräume gebildet. Der zwischen 90° und 180° liegende Hohlraum enthält ein maximal verdichtetes Gemisch zum Zündzeitpunkt. Aus dem zwischen 180° und 270° liegenden Hohlraum wurden die Verbrennungsgase ausgestoßen. Die Auslaßöffnung 38 wurde geschlossen. Bei einer Drehung des Kolbens 12 in Richtung des Pfeiles A wird die Einlaßöffnung 36 allmählich geöffnet, so daß in den zwischen 270° und 360° liegenden Hohlraum Gemisch angesaugt wird. In der unteren Hälfte dagegen hat der in Umlaufrichtung zwischen 270° und 90° gemessene Verbrennungsraum seine maximale Ausdehnung erreicht. Die Auslaßöffnung 38 ist offen. Der Kolben 12 befindet sich bezüglich der unteren Endfläche 20 in seinem unteren Totpunkt und der Ausschub der Verbrennungsgase aus dem Brennraum beginnt. In dem zweiten zwischen 90° und 270° liegenden Hohlraum wurde Gemisch angesaugt, das nun bei sich weiter drehendem Kolben verdichtet wird.Figure 5 shows the piston 12 at top dead center. Four separate cavities are formed between the upper end surface 20 of the annular space 14 and the upper end surface 26 of the piston 12. The cavity lying between 90 ° and 180 ° contains a maximum compressed mixture at the time of ignition. The combustion gases were expelled from the cavity between 180 ° and 270 °. The outlet opening 38 was closed. When the piston 12 rotates in the direction of arrow A, the inlet opening 36 is gradually opened, so that mixture is sucked into the cavity lying between 270 ° and 360 °. In the lower half, on the other hand, the combustion chamber measured in the direction of rotation between 270 ° and 90 ° has reached its maximum expansion. The outlet opening 38 is open. The piston 12 is at its bottom dead center with respect to the lower end face 20 and the exhaust of the combustion gases from the combustion chamber begins. Mixture was sucked into the second cavity between 90 ° and 270 °, which is now compressed as the piston continues to rotate.
Figur 6 zeigt die vorstehend angedeuteten Vorgänge bei einer Drehung des Kolbens 12 in Richtung des Pfeiles A relativ zu dem feststehenden Gehäuse 10. Die obere Einlaßöffnung 36 ist nun offen, so daß Gemisch angesaugt werden kann. Die Auslaßöffnung 38 ist geschlossen. Der Brennraum vergrößert sich mit den sich ausdehnenden Verbrennungsgasen. Im unteren Teil ist der Auslaßkanal vollständig geöffnet, so daß die Brenngase ausgeschoben werden können, während die Einlaßöffnung geschlossen ist und somit eine Verdichtung in dem angegebenen Bereich ermöglicht. Die Figur 8 zeigt die zu der Figur 5 inverse Stellung, d.h. der Kolben 12 befindet sich bezüglich der oberen Endfläche 20 des Ringraumes 14 in seiner unteren Totpunktstellung und bezüglich der unteren Endfläche 20 des Ringraumes 14 in seiner oberen Totpunktstellung. An die Figur 10 schließt sich dann wieder der in Figur 5 dargestellte Zustand an, in dem der Kolben 12 eine Umdrehung relativ zum Gehäuse und damit die vier Takte, nämlich Ansaugen, Verdichten, Verbrennen und Ausstoßen des Motors ausgeführt hat.FIG. 6 shows the processes indicated above when the piston 12 rotates in the direction of arrow A relative to the fixed housing 10. The upper inlet opening 36 is now open so that mixture can be sucked in. The outlet opening 38 is closed. The combustion chamber increases with the expanding combustion gases. In the lower part, the outlet channel is fully open so that the fuel gases can be pushed out, while the inlet opening is closed, thus allowing compression in the specified range. Figure 8 shows the position inverse to Figure 5, i.e. the piston 12 is in its lower dead center position with respect to the upper end face 20 of the annular space 14 and in its upper dead center position with respect to the lower end face 20 of the annular space 14. The state shown in FIG. 5 then follows FIG. 10 again, in which the piston 12 has made one revolution relative to the housing and thus the four cycles, namely suction, compression, combustion and ejection of the engine.
Man erkennt, daß die Steuerung der Einlaß- und Auslaßöffnungen vollständig ohne Ventile allein durch den Kolben selbst möglich ist und daß außer dem rotierenden und axial oszillierenden Kolben sowie der Welle keine weiteren beweglichen Teile erforderlich sind. Insbesondere werden keine beweglichen Dichtungselemente benötigt. Da der Kolben völlig symmetrisch aufgebaut ist, tritt auch keine Unwucht auf, welche die Lager oder die Welle beanspruchen würde.It can be seen that the control of the inlet and outlet openings is completely possible without valves by the piston itself and that besides that rotating and axially oscillating pistons and the shaft no further moving parts are required. In particular, no movable sealing elements are required. Since the piston is completely symmetrical, there is no imbalance that would stress the bearings or the shaft.
Die Figuren 11 bis 16 zeigen die gleichen Phasen für eine als Pumpe ausgebildete Drehkolbenmaschine. Da es hier nur zwei Takte pro Arbeitshub gibt, nämlich Ansaugen und Ausstoßen, können zwei Paare von Einlaßöffnung 36 (Saugleitung) und Auslaßöffnung 38 (Druckleitung) vorgesehen sein. Im übrigen ist die Arbeitsweise der beiden Kolben/Ringraumanordnungen wieder in der gleichen Weise um 180° gegeneinander versetzt, wie dies bereits bei dem Motor gemäß den Figuren 5 bis 10 beschrieben wurde. FIGS. 11 to 16 show the same phases for a rotary piston machine designed as a pump. Since there are only two cycles per working stroke, namely suction and ejection, two pairs of inlet opening 36 (suction line) and outlet opening 38 (pressure line) can be provided. For the rest, the operation of the two piston / annular space arrangements is again offset by 180 ° in the same way as has already been described for the engine according to FIGS. 5 to 10.

Claims

P a t e n t a n s p r ü c h eP a t e n t a n s r u c h e
Drehkolbenmaschine mit einem Gehäuse (10) und einem Kolben (12), der in einem Hohlraum des Gehäuses (10) drehbar angeordnet und mit einer das Gehäuse durchsetzenden Welle (18) drehfest verbunden ist, wobei in dem Gehäuse (10) jeweils mindestens ein Einlaß- und ein Auslaßkanal (32) zum Zufuhren bzw Abfuhren eines Arbeitsfluides zu bzw aus dem Hohlraum ausgebildet sind, dadurch gekennzeichnet, daß der Hohlraum einen Abschnitt in Form eines zur Welle (18) koaxialen zylindrischen Ringraumes (14) hat, daß der Kolben (12) als Ringkolben in Form eines zylindrischen Rohrabschnittes ausgebildet ist, der in den Ringraum (14) des Gehäuses (10) eingreift und in diesem axial verschiebbar gefuhrt ist und daß die einander zugekehrten Endflachen (20, 26) des Ringraumes (14) und des Ringkolbens (12) als stetige Wellenflachen mit achsparallel gerichteter Amplitude ausgebildet sind, wobei die Einlaß- und Auslaßoffnungen (36, 38) innerhalb eines axialen Bereiches der Ringraummantelfläche liegen, der durch den maximalen axialen Abstand der Wellentaler (24, 20) der einander zugewandten Endflachen (20, 26) bestimmt wirdRotary piston machine with a housing (10) and a piston (12) which is rotatably arranged in a cavity of the housing (10) and is non-rotatably connected to a shaft (18) passing through the housing, at least one inlet in each case in the housing (10) - And an outlet channel (32) for supplying or discharging a working fluid to or from the cavity are formed, characterized in that the cavity has a section in the form of a cylindrical annular space (14) coaxial with the shaft (18) that the piston (12 ) is designed as an annular piston in the form of a cylindrical tube section which engages in the annular space (14) of the housing (10) and is guided axially displaceably therein and that the mutually facing end faces (20, 26) of the annular space (14) and the annular piston (12) are designed as continuous wave surfaces with an axially parallel amplitude, the inlet and outlet openings (36, 38) lying within an axial region of the annular surface area s, which is determined by the maximum axial distance of the troughs (24, 20) of the mutually facing end faces (20, 26)
Drehkolbenmaschine nach Anspruch 1 , dadurch gekennzeichnet, daß mindestens zwei Wellenberge (22, 28) und zwei Wellentaler (24, 30) auf 360° des Umfangs vorgesehen sind, wobei die in Umfangsrichtung gemessene Halbwertsbreite der Wellenberge (28) mindestens einer der Endflachen kleiner als die der Wellentaler (30) derselben Endflache istRotary piston machine according to claim 1, characterized in that at least two wave crests (22, 28) and two wave troughs (24, 30) are provided over 360 ° of the circumference, the half-width of the wave crests (28) measured in the circumferential direction being smaller than at least one of the end faces which is the trough (30) of the same end surface
Drehkolbenmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Kolben (12) auf der Welle (18) axial verschiebbar gelagert istRotary piston machine according to claim 1 or 2, characterized in that the piston (12) is axially displaceably mounted on the shaft (18)
Drehkolbenmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Kolben (12) starr mit der Welle (18) verbunden und diese axial in dem Gehäuse (10) verschiebbar gelagert istRotary piston machine according to claim 1 or 2, characterized in that the piston (12) is rigidly connected to the shaft (18) and this is axially displaceably mounted in the housing (10)
Drehkolbenmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Kolben (12) in Richtung auf die Endflache (20) des Ringraumes (14) vorgespannt ist Rotary piston machine according to one of claims 1 to 4, characterized in that the piston (12) is prestressed in the direction of the end face (20) of the annular space (14)
6. Drehkolbenmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß in einer Mantelfläche des Kolbens (12) oder des Ringraumes (14) eine Nut (33) ausgebildet ist, in die ein mit dem jeweils anderen Teil (Ringraum (14), Kolben (12)) verbundenes Führungselement (35) eingreift, wobei der Verlauf der Nut in Umfangsrichtung dem der Wellenform der Endfläche (20) des Ringraumes (14) entspricht.6. Rotary piston machine according to one of claims 1 to 4, characterized in that in a lateral surface of the piston (12) or the annular space (14) is formed a groove (33) into which one with the other part (annular space (14) , Piston (12)) connected guide element (35) engages, the course of the groove in the circumferential direction corresponding to that of the waveform of the end face (20) of the annular space (14).
7. Drehkolbenmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß in einer der einander zugekehrten Endflächen (20, 26) von Ringraum (14) und Kolben (12) ein zur rollenden Anlage an der jeweils anderen Endfläche bestimmtes Führungselement (37) drehbar gelagert ist.7. Rotary piston machine according to one of claims 1 to 4, characterized in that in one of the mutually facing end faces (20, 26) of the annular space (14) and piston (12) a guide element (37) intended for rolling contact with the other end face. is rotatably mounted.
8. Drehkolbenmaschine nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Einlaßöffnung (36) und die Auslaßöffnung (38) in Umfangsrichtung vor bzw. hinter einem Wellenberg (22) der Endfläche (20) des Ringraumes (14) angeordnet sind.8. Rotary piston machine according to one of claims 1 to 7, characterized in that the inlet opening (36) and the outlet opening (38) are arranged in the circumferential direction in front of or behind a wave crest (22) of the end face (20) of the annular space (14).
9. Drehkolbenmaschine nach einem der Ansprüche 2 bis 8, dadurch gekennzeichnet, daß bei ihrer Verwendung als Pumpe jeweils mindestens zwei Einlaßöffnungen (36) und zwei Auslaßöffnungen (38) pro Endfläche des Kolbens (12) vorgesehen sind.9. Rotary piston machine according to one of claims 2 to 8, characterized in that when used as a pump at least two inlet openings (36) and two outlet openings (38) are provided per end face of the piston (12).
10. Drehkolbenmaschine nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die Einlaßöffnung und/oder die Auslaßöffnung an der radial inneren Begrenzungswand (15) des Ringraumes (14) vorgesehen ist.10. Rotary piston machine according to one of claims 1 to 9, characterized in that the inlet opening and / or the outlet opening is provided on the radially inner boundary wall (15) of the annular space (14).
11. Drehkolbenmaschine nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß eine der miteinander in Berührung tretenden Endflächen (20, 26) sinusförmig ausgebildet ist.11. Rotary piston machine according to one of claims 1 to 10, characterized in that one of the contacting end faces (20, 26) is sinusoidal.
12. Drehkolbenmaschine nach einem der Ansprüche 1 bis 11 , dadurch gekennzeichnet, daß zwei Ringraum/Ringkolbenanordnungen (14, 12) nach einem der Ansprüche 1 bis 5 koaxial zueinander so angeordnet sind, daß die beiden auf derselben Welle (18) angeordneten Kolben (12) sich gemeinsam zwischen den Endfächen (20) der beiden Ringräume (14) bewegen.12. Rotary piston machine according to one of claims 1 to 11, characterized in that two annular space / annular piston arrangements (14, 12) according to one of claims 1 to 5 are arranged coaxially to one another so that the two pistons (12) arranged on the same shaft (18) ) yourself move together between the end faces (20) of the two annular spaces (14).
13. Drehkolbenmaschine nach Anspruch 12, dadurch gekennzeichnet, daß die beiden Kolben einen einstückigen Doppelkolben (12) bilden.13. Rotary piston machine according to claim 12, characterized in that the two pistons form a one-piece double piston (12).
14. Drehkolbenmaschine nach Anspruch 12 oder 13, dadurch gekennzeichnet, daß die Maxima und Minima der beiden identisch geformten Endflächen (20) des Ringraumes (14) jeweils auf denselben Erzeugenden der zylindrischen Mantelfläche des Ringraumes (14) liegen und daß das Maximum (28) der einen Endfläche (26) der beiden Kolben (12) mit einem Minimum (30) der anderen Endfläche (26) gemeinsam auf einer Erzeugenden der Kolbenmantelfläche liegt. 14. Rotary piston machine according to claim 12 or 13, characterized in that the maxima and minima of the two identically shaped end faces (20) of the annular space (14) each lie on the same generatrix of the cylindrical outer surface of the annular space (14) and that the maximum (28) one end face (26) of the two pistons (12) with a minimum (30) of the other end face (26) lies jointly on a generatrix of the piston outer surface.
EP00974505A 1999-11-04 2000-11-03 Rotary piston machine Expired - Lifetime EP1226338B1 (en)

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DE19953168A DE19953168A1 (en) 1999-11-04 1999-11-04 Rotary lobe machine
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Families Citing this family (4)

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DE10156835C1 (en) * 2001-11-20 2003-04-30 Peter Schnabl Rotary piston pump for conveying media comprises an annular piston having control pockets opening toward its axial end surface for controlling inlet and outlet openings
DE102004019373B4 (en) * 2004-04-21 2013-04-18 Peter Schnabl Rotary engine
US8336409B2 (en) * 2008-12-11 2012-12-25 Magnamotor, Llc Magnetic piston apparatus and method
GR20180100001A (en) * 2018-01-03 2019-09-06 Γεωργιτζικη, Ελπιδα Γεωργιου Mechanism converting the oscillatory motion into rotary and vice versa - applications of said mechanism

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1430602A (en) * 1921-04-29 1922-10-03 Sykora Rudolf Rotary pump
US2517279A (en) * 1944-04-06 1950-08-01 Benzler Bengt Lennart Control device for rotary reciprocating engines
US3667876A (en) * 1970-12-21 1972-06-06 Michael David Boyd Rotary fluid flow machines
DE2733574A1 (en) * 1977-07-26 1979-02-08 Hans Frank Rotary piston IC engine - has two coaxial opposed rotating pistons in one cylinder and with scroll faces shuttling free piston between them
BR7805823A (en) * 1978-09-06 1981-10-27 C Parente ROTATING PUMP OF OSCILLATING PUMP IN AXIAL DIRECTION WITH FLOW CONTROL AND REVERSION
GB2075122A (en) * 1980-04-14 1981-11-11 Jayasooriya L Rotary positive-displacement fluid-machines
GB8922993D0 (en) * 1989-10-12 1989-11-29 Richards Kevin Pump or motor
EP0597855B1 (en) * 1991-08-06 1996-12-27 GOODMAN, William A. Circular rotary engine
JP4056600B2 (en) * 1996-11-19 2008-03-05 幸男 梶野 Disc type rotation engine
CA2215219C (en) * 1996-11-19 2000-07-04 Yukio Kajino Disc-type rotary engine
IT1288494B1 (en) 1996-11-20 1998-09-22 Sasib Spa METHOD AND DEVICE FOR THE CONTROL WITHOUT DIRECT CONTACT OF THE HEADS OF THE CIGARETTES, OR SIMILAR.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0133047A1 *

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WO2001033047A1 (en) 2001-05-10

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