EP1749145B1 - Control of gap loss flow in a gear machine - Google Patents

Control of gap loss flow in a gear machine Download PDF

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Publication number
EP1749145B1
EP1749145B1 EP05756080.7A EP05756080A EP1749145B1 EP 1749145 B1 EP1749145 B1 EP 1749145B1 EP 05756080 A EP05756080 A EP 05756080A EP 1749145 B1 EP1749145 B1 EP 1749145B1
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EP
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Prior art keywords
rotor
rotors
rotary piston
axial
piston machine
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EP05756080.7A
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German (de)
French (fr)
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EP1749145A1 (en
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Felix Arnold
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F01C3/08—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/601—Adjustment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • the invention is based on a rotary piston machine, which can operate as a pump, compressor or motor, according to the preamble of the main claim.
  • a known rotary engine DE PS 42 41 320 .
  • EP PS 1 005 604 is also sought by the design of the teeth, a high tightness between the work spaces to obtain the lowest possible leakage currents from a working space to the adjacent working space on the edges with line contact between the interacting teeth of the rotors.
  • the tooth combs of a rotor run linearly on the flanks of a cycloidal development of the tread having other rotor from.
  • a known rotary engine of the generic type ( DE 10 2004 044 297 A1 ) is the drive rotor by a Electric motor driven, whereby there is a major problem avoiding short circuits between the work spaces in the area of the line-shaped contact.
  • the output rotor is loaded to reduce the gap in the area of the line-shaped contact in the direction of the drive rotor.
  • the advantages of the invention are that the rotors are arranged sealingly to each other in order to reduce gap losses. A forming gap flow is suppressed and achieved an additional sealing effect by pressing resulting pressure forces on all sides on the rotors. Again, it is primarily about the prevention of slit flows.
  • the rotary piston engine according to the invention with the characterizing features of the main claim has the advantage that the energy consumption of the rotary piston engine directly corresponds to the actual power output of the same. From a never quite avoidable gap loss of such a machine is given by targeted change in the gap width quantity control, or loss amount control has become.
  • An additional advantage is that, for example in the promotion of fuels or oil, foaming is largely prevented, which may arise, for example, in the control of a return flow channel.
  • the displaceable rotor is arranged coaxially with the cylindrical control chamber.
  • the force is arbitrarily controlled and works with hydraulic, gaseous and / or electrical means. It is crucial that counteract the pressures in the work spaces forces on the back of the rotor to control the desired axial displacement of the rotor and thus the leakage current between the work spaces.
  • the space bounded by the rear side of the rotor is pressure-tightly closed in order to generate the actuating force by means of a liquid or gaseous medium.
  • the invention is used to generate the force to be conveyed medium.
  • the delivery pressure of the machine can be used directly to control the force.
  • one of the rotors (wave rotor) on its side facing away from the working spaces is spherical and mounted in a corresponding spherical recess in the housing.
  • this spherical sphere can cut the radial bearing of the rotor to set its axial axis of rotation.
  • a spherical surface on a rotor is present on the rotors in the central end face region centrally, which is mounted on a corresponding spherical recess on the other rotor and limits the work spaces radially inwardly.
  • a connection for the leakage current between the work spaces is additionally established over this area.
  • the exemplary embodiment is a fuel delivery pump shown in longitudinal section.
  • an inlay 2 is arranged secured against rotation, in which rotatable and radially guided and axially displaceably a counter rotor 3 is arranged, which cooperates with a shaft rotor 4 driven from outside the pump.
  • Shaft rotor 4 and counter rotor 3 have on the mutually facing end face an interlocking toothing, are separated by the work spaces in a known manner from each other and on the Counter rotor 3 is driven by the shaft rotor 4.
  • One of the two serrations has a cycloidal cross section to thereby form a linear connection between the tooth crests of the other part and this cycloidal surface.
  • suction kidney suction kidney
  • Druckniere pressure channel
  • the counter rotor 3 is rotatably arranged in a plain bearing bush 5, wherein between the plain bearing bush 5 and the counter rotor 3, a slide bearing shaft 6 is arranged, which is mounted radially and axially in the plain bearing bush 5 and axially displaceable including the counter rotor 3 within the plain bearing bushing 5.
  • the shaft rotor 4 is mounted radially and axially in a sliding bearing 7, wherein between the shaft rotor 4 and the plain bearing bush 7, the hat-shaped end of a drive shaft 8 projects, the shaft rotor 4 is immersed with a corresponding cylindrical portion in this hat-shaped formation.
  • a spring 10 is arranged, which serves on the one hand to entrain the shaft rotor 4 during the rotational movement of the shaft 8 and on the other hand, the shaft rotor 4 loaded in the direction counter rotor 3.
  • the housing 1 is closed on the side facing away from the shaft 8 by covers 11 and 12, wherein the inner lid 11 is supported on the one hand on the plain bearing bushing 5 and on the other hand on the outer cover 12, which serves as the actual closure part of the housing 1 of the pump and to the outside is secured by a retaining ring 9 in its axial position.
  • the counter rotor 3 is axially displaceable in the direction of its axis of rotation.
  • This shift can be carried out according to the invention by appropriate means, wherein the pressure developing in the working spaces forms a corresponding force acting on the counter rotor 3 adjusting.
  • This adjusting force counteracts the illustrated embodiment, a restoring force formed by liquid, which acts on the facing away from the working spaces of the counter rotor in the plain bearing bushing 5.
  • To control this reaction force is a connection, not shown, between these spaces available, the forces, in particular due to the applied surfaces, must be coordinated.
  • an insert 13 is sealingly arranged in the inlay 2, which serves for the axial retention of the slide bearing 7 and also for receiving a mechanical seal 17, in which the shaft 8 is rotatably arranged.
  • the shaft 8 is also mounted in this inlay insert 13 via a ball bearing 18, wherein between inlay insert 13 and inlay 2 and between inlay 2 and housing 1 O-rings 16 provide the required seal.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Drehkolbenmaschine, die als Pumpe, Verdichter oder Motor arbeiten kann, nach dem Oberbegriff des Hauptanspruchs. Bei einer Solchen bekannten Drehkolbenmaschine ( DE PS 42 41 320 , EP PS 1 005 604 ) ist, auch durch die Gestaltung der Zähne, eine hohe Dichtheit zwischen den Arbeitsräumen angestrebt, um möglichst geringe Verlustströme von einem Arbeitsraum zum danebenliegenden Arbeitsraum über die Flanken mit Linienberührung zwischen den zusammenwirkenden Zähnen der Rotoren zu erhalten. Hierbei laufen die Zahnkämme des einen Rotors linienförmig an den Flanken des eine zykloidische Abwicklung der Lauffläche aufweisenden anderen Rotors ab.The invention is based on a rotary piston machine, which can operate as a pump, compressor or motor, according to the preamble of the main claim. In such a known rotary engine ( DE PS 42 41 320 . EP PS 1 005 604 ) is also sought by the design of the teeth, a high tightness between the work spaces to obtain the lowest possible leakage currents from a working space to the adjacent working space on the edges with line contact between the interacting teeth of the rotors. Here, the tooth combs of a rotor run linearly on the flanks of a cycloidal development of the tread having other rotor from.

Je nach Einsatz solcher Drehkolbenmaschinen ändert sich die geforderte Leistung während des Betriebs, wofür unterschiedliche Steuer- oder Regelungsverfahren bekannt sind. Die einfachste Methode ist Druckseite und Saugseite der Maschine zu verbinden, was jedoch bezüglich der von der Maschine aufgenommenen hohen Energie kaum einen Unterschied bedeutet. In vielen Fällen, insbesondere beim Einsatz als Schmierpumpe in der Kfz-Branche, aber auch als Vorförderpumpe für Dieseleinspritzeinlagen, ist angestrebt, die Energieaufnahme der Maschine so gering wie möglich zu halten und der tatsächlichen Leistungsabgabe derselben anzupassen (siehe DE OS 100 25 723 ).Depending on the use of such rotary engines changes the required power during operation, for which different control or regulating methods are known. The simplest method is to connect the pressure side and the suction side of the machine, which, however, makes little difference to the high energy absorbed by the machine. In many cases, especially when used as a lubrication pump in the automotive industry, but also as a pre-feed pump for diesel injector, the aim is to keep the power consumption of the machine as low as possible and the actual power output of the same adapt (see DE OS 100 25 723 ).

Bei einer bekannten Drehkolbenmaschine der gattungsgemäßen Art ( DE 10 2004 044 297 A1 ) wird der Antriebsrotor durch einen Elektromotor angetrieben, wobei auch hier ein Hauptproblem die Vermeidung von Kurzschlüssen zwischen den Arbeitsräumen im Bereich der linienförmigen Berührung bestehen. So ist, wie unter 0012 bis 0014 der Druckschrift DE OS 10 2004 044 297 , dargestellt, dass der Abtriebsrotor zur Reduzierung des Spaltes im Bereich der linienförmigen Berührung in Richtung des Antriebsrotors belastet ist. Auch bei der Beschreibung einer anderen bekannten Drehkolbenmaschine der gattungsgemäßen Art ( DE 103 35 939 A1 ) wird auf Seite 2 darauf hingewiesen, dass die Vorteile der Erfindung darin bestehen, dass die Rotoren zueinander dichtend angeordnet sind, um Spaltverluste zu verringern. Eine sich ausbildende Spaltströmung wird unterbunden und eine zusätzliche Dichtwirkung erzielt, indem resultierende Druckkräfte allseitig auf die Rotoren drücken. Auch hier geht es in erster Linie um das Unterbinden von Spaltströmungen.In a known rotary engine of the generic type ( DE 10 2004 044 297 A1 ) is the drive rotor by a Electric motor driven, whereby there is a major problem avoiding short circuits between the work spaces in the area of the line-shaped contact. Such is as under 0012 to 0014 of the document DE OS 10 2004 044 297 , that the output rotor is loaded to reduce the gap in the area of the line-shaped contact in the direction of the drive rotor. Also in the description of another known rotary engine of the generic type ( DE 103 35 939 A1 ) it is pointed out on page 2 that the advantages of the invention are that the rotors are arranged sealingly to each other in order to reduce gap losses. A forming gap flow is suppressed and achieved an additional sealing effect by pressing resulting pressure forces on all sides on the rotors. Again, it is primarily about the prevention of slit flows.

Die Erfindung und ihre VorteileThe invention and its advantages

Die erfindungsgemäße Drehkolbenmaschine mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, dass die Energieaufnahme der Drehkolbenmaschine unmittelbar der tatsächlichen Leistungsabgabe derselben entspricht. Aus einem nie ganz vermeidbaren Spaltverlust einer solchen Maschine ist eine durch gezielte Änderung der Spaltbreite gegebene Mengensteuerung, bzw. Verlustmengensteuerung geworden. Ein zusätzlicher Vorteil besteht darin, dass, beispielsweise bei Förderung von Kraftstoffen oder Öl, ein Aufschäumen weitgehend unterbunden wird, was beispielsweise bei der Steuerung eines Rückstromkanals entstehen kann.The rotary piston engine according to the invention with the characterizing features of the main claim has the advantage that the energy consumption of the rotary piston engine directly corresponds to the actual power output of the same. From a never quite avoidable gap loss of such a machine is given by targeted change in the gap width quantity control, or loss amount control has become. An additional advantage is that, for example in the promotion of fuels or oil, foaming is largely prevented, which may arise, for example, in the control of a return flow channel.

Es ist zwar bei Förderpumpen bekannt, durch unmittelbares Verbinden von Saug- und Druckseite eine entsprechende Verringerung der Energieaufnahme zu erzielen ( DE 100 25 723 ), nur handelt es sich hierbei nicht um auf den Stirnseiten der Rotoren gelegene Arbeitsräume, sondern um Zahnradpumpen mit radial angeordneten Zähnen oder Zahnringen mit einer von vornherein völlig anderen Arbeitsweise (Verdrängung in Axialrichtung), so dass derartige vielfältig bekannte Lösungen nicht bei der Erfindung Anwendung finden können. So ist es bei einer ebenfalls mit Zahnrad und Zahnring arbeitenden Ölpumpe bekannt ( US PS 5,085,187 ), die Pumpenarbeitsräume seitlich durch einen Deckel zu verschließen, der bei ausreichendem Förderdruck verschoben und eine Verbindung zwischen dem Saugraum und Druckraum der Ölpumpe herstellt.Although it is known in feed pumps, by directly connecting the suction and pressure side to achieve a corresponding reduction in energy consumption ( DE 100 25 723 ), only these are not located on the front sides of the rotors working spaces, but gear pumps with radially arranged teeth or toothed rings with a completely different operation from the outset (displacement in the axial direction), so that such diverse known solutions not in the invention application can find. So it is known in a likewise working with gear and ring gear oil pump ( U.S. Patent 5,085,187 ) To close the pump working spaces laterally by a lid which moves at sufficient delivery pressure and establishes a connection between the suction chamber and the pressure chamber of the oil pump.

Zur Anpassung der Energieaufnahme an die tatsächliche Leistungsabgabe ist es bekannt, bei Drehkolbenmaschinen mit stirnseitiger Verzahnung ( US PS 2,049,775 ) den Abtriebsrotor innerhalb seiner kugeligen Lagerung zu verschwenken, um dadurch den axialen Winkel zwischen den Drehachsen zu verändern, was entsprechend zu einer Fördermengenänderung bis hin zu Null-Förderung führen kann. Der Nachteil einer solchen Konstruktion besteht nicht nur in dem erheblichen höheren konstruktiven Aufwand und der stärker begrenzten Leistungsfähigkeit, sondern vor allem in der Abdichtung der Arbeitsräume zu der Verstelleinrichtung hin.To adapt the energy consumption to the actual power output, it is known in rotary engines with frontal toothing ( US Pat. No. 2,049,775 ) to pivot the output rotor within its spherical bearing, thereby changing the axial angle between the axes of rotation, which can lead to a delivery rate change to zero promotion accordingly. The disadvantage of such a construction is not only in the considerable higher design effort and the more limited performance, but especially in the sealing of the work spaces to the adjustment.

Nach einer vorteilhaften Ausgestaltung der Erfindung ist mindestens der axial verschiebbare Rotor in einem entsprechend zylindrischen Steuerraum des Maschinengehäuses axial und radial geführt. Der verschiebbare Rotor ist dabei achsgleich mit dem zylindrischen Steuerraum angeordnet.According to an advantageous embodiment of the invention, at least the axially displaceable rotor in a correspondingly cylindrical control chamber of the machine housing axially and radially guided. The displaceable rotor is arranged coaxially with the cylindrical control chamber.

Nach der Erfindung ist die Stellkraft willkürlich steuerbar und arbeitet mit hydraulischen, gasförmigen und/oder elektrischen Mitteln. Maßgebend ist, dass den Drücken in den Arbeitsräumen Kräfte auf der Rückseite des Rotors entgegenwirken, um die gewünschte axiale Verstellung des Rotors und damit den Verluststrom zwischen den Arbeitsräumen zu steuern.According to the invention, the force is arbitrarily controlled and works with hydraulic, gaseous and / or electrical means. It is crucial that counteract the pressures in the work spaces forces on the back of the rotor to control the desired axial displacement of the rotor and thus the leakage current between the work spaces.

Nach einer zusätzlichen Ausgestaltung der Erfindung ist der von der Rückseite des Rotors begrenzte Raum druckdicht geschlossen, um mittels eines flüssigen oder gasförmigen Mediums die Stellkraft zu erzeugen.According to an additional embodiment of the invention, the space bounded by the rear side of the rotor is pressure-tightly closed in order to generate the actuating force by means of a liquid or gaseous medium.

Nach einer diesbezüglichen vorteilhaften Ausgestaltung der Erfindung dient zur Erzeugung der Stellkraft das zu fördernde Medium. Hierdurch kann der Förderdruck der Maschine unmittelbar zur Regelung der Stellkraft verwendet werden. Entsprechend besteht nach einer Ausgestaltung der Erfindung eine Verbindung für das zu fördernde Medium zwischen den Arbeitsräumen und dem Steuerraum.According to a related advantageous embodiment of the invention is used to generate the force to be conveyed medium. As a result, the delivery pressure of the machine can be used directly to control the force. Accordingly, according to one embodiment of the invention, a connection for the medium to be conveyed between the work spaces and the control room.

Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung ist einen der Rotoren (Wellenrotor) auf seiner den Arbeitsräumen abgewandten Seite kugelsphärisch ausgebildet und in einer entsprechend kugeligen Ausnehmung im Gehäuse gelagert. In diese Kugelsphäre kann die radiale Lagerung des Rotors einschneiden um dessen axiale Drehachse festzulegen.According to an additional advantageous embodiment of the invention, one of the rotors (wave rotor) on its side facing away from the working spaces is spherical and mounted in a corresponding spherical recess in the housing. In this spherical sphere can cut the radial bearing of the rotor to set its axial axis of rotation.

Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung ist an den Rotoren im mittleren Stirnseitenbereich zentral eine Kugelfläche an einem Rotor vorhanden, die auf einer entsprechenden sphärischen Ausnehmung am anderen Rotor gelagert ist und die Arbeitsräume radial nach innen begrenzt. Bei der axialen Verschiebung des einen Rotors wird über diesen Bereich zusätzlich eine Verbindung für den Verluststrom zwischen den Arbeitsräumen hergestellt.According to an additional advantageous embodiment of the invention, a spherical surface on a rotor is present on the rotors in the central end face region centrally, which is mounted on a corresponding spherical recess on the other rotor and limits the work spaces radially inwardly. During the axial displacement of the one rotor, a connection for the leakage current between the work spaces is additionally established over this area.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention are the following description, the drawings and claims removed.

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im Folgenden näher beschrieben. Beim Ausführungsbeispiel handelt es sich um eine im Längsschnitt dargestellte Kraftstoffförderpumpe.An embodiment of the object of the invention is illustrated in the drawing and described in more detail below. The exemplary embodiment is a fuel delivery pump shown in longitudinal section.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In einem Gehäuse 1 ist ein Inlay 2 verdrehgesichert angeordnet, in welchem verdrehbar und radial geführt und axial verschiebbar ein Gegenrotor 3 angeordnet ist, der mit einem von außerhalb der Pumpe angetriebenen Wellenrotor 4 zusammenwirkt. Wellenrotor 4 und Gegenrotor 3 weisen auf der einander zugewandten Stirnseite eine ineinandergreifende Verzahnung auf, durch die in bekannter Weise Arbeitsräume voneinander getrennt werden und über die der Gegenrotor 3 durch den Wellenrotor 4 angetrieben wird. Eine von den beiden Stirnverzahnungen weist einen zykloidischen Querschnitt auf, um dadurch eine linienförmige Verbindung zwischen den Zahnkämmen des anderen Teils und dieser zykloidischen Oberfläche zu bilden. Die hier im Einzelnen nicht dargestellten Arbeitsräume, die sich auf Grund des zwischen den Drehachsen der Rotoren 3 und 4 eingeschlossenen Winkels während des Betriebs in ihrem Volumen laufend ändern, sind entsprechend der Förderaufgabe mit einem Saugkanal (Saugniere) und einem Druckkanal (Druckniere) verbunden.In a housing 1, an inlay 2 is arranged secured against rotation, in which rotatable and radially guided and axially displaceably a counter rotor 3 is arranged, which cooperates with a shaft rotor 4 driven from outside the pump. Shaft rotor 4 and counter rotor 3 have on the mutually facing end face an interlocking toothing, are separated by the work spaces in a known manner from each other and on the Counter rotor 3 is driven by the shaft rotor 4. One of the two serrations has a cycloidal cross section to thereby form a linear connection between the tooth crests of the other part and this cycloidal surface. The working spaces, not shown here in detail, which constantly change in their volume due to the included between the axes of rotation of the rotors 3 and 4 angle during operation, are connected according to the conveying task with a suction channel (suction kidney) and a pressure channel (Druckniere).

Der Gegenrotor 3 ist in einer Gleitlagerbuchse 5 verdrehbar angeordnet, wobei zwischen der Gleitlagerbuchse 5 und dem Gegenrotor 3 eine Gleitlagerwelle 6 angeordnet ist, die in der Gleitlagerbuchse 5 radial und axial gelagert ist und einschließlich dem Gegenrotor 3 innerhalb der Gleitlagerbuchse 5 axial verschiebbar ist.The counter rotor 3 is rotatably arranged in a plain bearing bush 5, wherein between the plain bearing bush 5 and the counter rotor 3, a slide bearing shaft 6 is arranged, which is mounted radially and axially in the plain bearing bush 5 and axially displaceable including the counter rotor 3 within the plain bearing bushing 5.

Auch der Wellenrotor 4 ist in einem Gleitlager 7 radial und axial gelagert, wobei zwischen dem Wellenrotor 4 und der Gleitlagerbuchse 7 das hutförmig ausgebildete Ende einer Antriebswelle 8 ragt, wobei der Wellenrotor 4 mit einem entsprechenden zylindrischen Abschnitt in diese hutförmige Ausbildung eintaucht. Zwischen dem Boden des hutförmigen Abschnitts der Antriebswelle 8 und dem eintauchenden Abschnitt des Wellenrotors 4 ist eine Feder 10 angeordnet, die einerseits zur Mitnahme des Wellenrotors 4 bei der Drehbewegung der Welle 8 dient und andererseits den Wellenrotor 4 in Richtung Gegenrotor 3 belastet.Also, the shaft rotor 4 is mounted radially and axially in a sliding bearing 7, wherein between the shaft rotor 4 and the plain bearing bush 7, the hat-shaped end of a drive shaft 8 projects, the shaft rotor 4 is immersed with a corresponding cylindrical portion in this hat-shaped formation. Between the bottom of the hat-shaped portion of the drive shaft 8 and the dipping portion of the shaft rotor 4, a spring 10 is arranged, which serves on the one hand to entrain the shaft rotor 4 during the rotational movement of the shaft 8 and on the other hand, the shaft rotor 4 loaded in the direction counter rotor 3.

Das Gehäuse 1 ist auf der der Welle 8 abgewandten Seite durch Deckel 11 und 12 verschlossen, wobei der innengelegene Deckel 11 sich einerseits an der Gleitlagerbuchse 5 und andererseits am außenliegenden Deckel 12 abstützt, der als eigentliches Verschlussteil des Gehäuses 1 der Pumpe dient und nach außen durch einen Sicherungsring 9 in seiner axialen Lage gesichert ist.The housing 1 is closed on the side facing away from the shaft 8 by covers 11 and 12, wherein the inner lid 11 is supported on the one hand on the plain bearing bushing 5 and on the other hand on the outer cover 12, which serves as the actual closure part of the housing 1 of the pump and to the outside is secured by a retaining ring 9 in its axial position.

Erfindungsgemäß ist der Gegenrotor 3 axial in Richtung seiner Drehachse verschiebbar. Diese Verschiebung kann erfindungsgemäß durch entsprechende Mittel erfolgen, wobei der sich in den Arbeitsräumen entwickelnde Druck eine entsprechende am Gegenrotor 3 angreifende Verstellkraft bildet. Dieser Verstellkraft wirkt dem dargestellten Ausführungsbeispiel eine durch Flüssigkeit gebildete Rückstellkraft entgegen, die den in die Gleitlagerbuchse 5 tauchenden, den Arbeitsräumen abgewandten Abschnitt des Gegenrotors beaufschlagt. Zur Steuerung dieser Gegenkraft ist eine nicht dargestellte Verbindung zwischen diesen Räumen vorhanden, wobei die Kräfte, insbesondere auf Grund der beaufschlagten Flächen, aufeinander abgestimmt sein müssen.According to the counter rotor 3 is axially displaceable in the direction of its axis of rotation. This shift can be carried out according to the invention by appropriate means, wherein the pressure developing in the working spaces forms a corresponding force acting on the counter rotor 3 adjusting. This adjusting force counteracts the illustrated embodiment, a restoring force formed by liquid, which acts on the facing away from the working spaces of the counter rotor in the plain bearing bushing 5. To control this reaction force is a connection, not shown, between these spaces available, the forces, in particular due to the applied surfaces, must be coordinated.

Im Bereich der Welle 8 ist im Inlay 2 ein Einsatz 13 dichtend angeordnet, der zur axialen Halterung der Gleitlager 7 dient und außerdem zur Aufnahme einer Gleitringdichtung 17, in welcher die Welle 8 drehbar angeordnet ist. Die Welle 8 ist außerdem in diesem Inlayeinsatz 13 über ein Kugellager 18 gelagert, wobei zwischen Inlayeinsatz 13 und Inlay 2 sowie zwischen Inlay 2 und Gehäuse 1 Rundschnurringe 16 für die erforderliche Abdichtung sorgen.In the area of the shaft 8, an insert 13 is sealingly arranged in the inlay 2, which serves for the axial retention of the slide bearing 7 and also for receiving a mechanical seal 17, in which the shaft 8 is rotatably arranged. The shaft 8 is also mounted in this inlay insert 13 via a ball bearing 18, wherein between inlay insert 13 and inlay 2 and between inlay 2 and housing 1 O-rings 16 provide the required seal.

Claims (7)

  1. Rotary piston machine which operates as a pump, compressor and/or motor,
    - having at least two movable rotary pistons which interact with a drive rotor (4) and an output drive rotor (3) and the rotational axes of which are at a defined axial angle with respect to one another,
    - having teeth which mesh into one another on the mutually facing end sides of the rotors (3, 4),
    - having a machine housing (1, 2) and a radial and axial mounting of the rotors (3, 4) in the machine housing (1, 2) which delimits working spaces with axial end sides of the rotors,
    - having a suction channel and a pressure channel in the machine housing (1, 2), which channels can be connected intermittently to the working spaces during running of the rotors (3, 4),
    - the mounting of at least one of the rotors (3, 4) in the machine housing (1, 2) having an axial adjustability in the direction of the rotational axis of the rotor (3),
    - an axial actuating force acting on the said rotor (3), which axial actuating force counteracts the force which is brought about by the working pressure in the working space and acts on the rotor (3),
    characterized in that
    the rotary piston machine has hydraulic, gaseous and/or electric means which act on that section of the rotor (3) which faces away from the working spaces and change the magnitude of the said actuating force in such a way that, by way of axial displacement of the rotor (3) in the axial direction, a predefined short-circuit gap is set between the working spaces which are separated from one another by the teeth of the rotors and, as a result, quantity control or lost-quantity control is achieved.
  2. Rotary piston machine according to Claim 1, characterized in that at least the axially displaceable rotor (3) is guided axially and radially in a correspondingly cylindrical control space of the machine housing (2).
  3. Rotary piston machine according to Claim 1 or 2, characterized in that the cylindrical control space can be closed in a pressure-tight manner.
  4. Rotary piston machine according to one of the preceding claims, characterized in that the medium to be delivered serves to generate the actuating force.
  5. Rotary piston machine according to Claim 4, characterized in that there is a connection between the working spaces and the control space for the medium to be delivered.
  6. Rotary piston machine according to one of the preceding claims, characterized in that one of the rotors (4), of spherical configuration on its side which faces away from the working spaces, is mounted in a correspondingly spherical recess in the housing (2).
  7. Rotary piston machine according to one of the preceding claims, characterized in that, on the rotors (3, 4), there is a spherical face on a rotor in the central end-side region, which spherical face is mounted on a corresponding spherical recess on the other rotor and delimits the working spaces radially towards the centre.
EP05756080.7A 2004-05-25 2005-05-19 Control of gap loss flow in a gear machine Active EP1749145B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004026048A DE102004026048A1 (en) 2004-05-25 2004-05-25 Gap leakage current control
PCT/DE2005/000934 WO2005116403A1 (en) 2004-05-25 2005-05-19 Control of gap loss flow in a gear machine

Publications (2)

Publication Number Publication Date
EP1749145A1 EP1749145A1 (en) 2007-02-07
EP1749145B1 true EP1749145B1 (en) 2013-07-17

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US (1) US20070253851A1 (en)
EP (1) EP1749145B1 (en)
JP (1) JP5244385B2 (en)
DE (1) DE102004026048A1 (en)
ES (1) ES2425363T3 (en)
WO (1) WO2005116403A1 (en)

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DE102008042564A1 (en) * 2008-10-02 2010-04-08 Robert Bosch Gmbh delivery unit
US9115646B2 (en) 2010-06-17 2015-08-25 Exponential Technologies, Inc. Shroud for rotary engine
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DE102020124825A1 (en) 2020-09-23 2022-03-24 Kolektor Group D.O.O. motor-pump unit
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Also Published As

Publication number Publication date
ES2425363T3 (en) 2013-10-15
WO2005116403A1 (en) 2005-12-08
DE102004026048A1 (en) 2005-12-29
US20070253851A1 (en) 2007-11-01
JP5244385B2 (en) 2013-07-24
EP1749145A1 (en) 2007-02-07
JP2008500482A (en) 2008-01-10

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