EP1859170B1 - Rotary piston machine - Google Patents

Rotary piston machine Download PDF

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Publication number
EP1859170B1
EP1859170B1 EP06722634.0A EP06722634A EP1859170B1 EP 1859170 B1 EP1859170 B1 EP 1859170B1 EP 06722634 A EP06722634 A EP 06722634A EP 1859170 B1 EP1859170 B1 EP 1859170B1
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EP
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Prior art keywords
housing
machine housing
driving part
driven part
machine
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EP06722634.0A
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German (de)
French (fr)
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EP1859170A1 (en
Inventor
Felix Arnold
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • 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
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type 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
    • F04C3/085—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type 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 the axes of cooperating members being on the same plane
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a rotary piston engine according to the preamble of the main claim.
  • a rotary engine with frontal toothing of a drive part and a driven part and located between the teeth workrooms that enlarge and reduce during rotation, whereby the conveying effect of the medium is generated has already been proposed several times.
  • DE 103 35 939 A1 are to reduce gap losses between the rotors in the axial and radial directions freely displaced, such gap losses may be both manufacturing but also result of shocks such a rotary piston machine during operation and thereby given unwanted changing the position of the rotors in their arrangement.
  • the additional contact pressure proposed there is also of little help from the pressure of the fluid flow.
  • the output member is loaded in the direction of the drive part, thereby to achieve the desired for use as a feed pump of gasoline injection engine assembly between the motor housing and the machine housing.
  • the axial clearance can be reduced but a basic setting or a corresponding flexibility for adjusting the pump is not given.
  • the invention has for its object to improve a rotary piston engine of the generic type so that it is particularly inexpensive to produce, allows a basic setting and a clamping of the rotors is avoided even when shaken during operation.
  • the rotary piston engine according to the invention is defined by the main claim.
  • the invention has the advantages mentioned in the underlying task. Depending on the type of fixing the floor bearing combined with it, that drive part and output part within arranged on the machine housing and enclosed by the floor bearings, on the one hand a subsequent adjustment of the game can be made, up to a basic setting, and on the other hand, a subsequent undesired clamping of the running parts can be prevented, also because a unit between the bottom bearing and machine housing. So there remains a required axial clearance.
  • the drive part and / or driven part on the side facing away from the pump chamber on a journal has a ring-shaped central bearing bore for receiving the journal.
  • the fuel delivery pump shown has a rotary piston pump 1 and an electric motor 2 driving this, which are arranged in a motor housing 3 and a housing cover 4 attached thereto.
  • the electric motor is shown greatly simplified with a rotor 5 and a magnetic ring 6, and an axial closure part 7 of the motor housing 3, which is connected thereto and sealed to this.
  • a rotary bearing 8 of the rotor 5 is provided on this closure part 7.
  • the electric motor 5, 6 flows around its cooling by the fuel within the motor housing 3.
  • the second pivot bearing of the rotor 5 is provided at its shaft end 9 in a bearing bore 10 of a bottom bearing 11, which is arranged in a corresponding opening on the end face of a machine housing 12 of the rotary lobe pump 1 and on which a frontally toothed drive part 13 of the pump on the Can axially support motor facing sides.
  • This machine housing 12 is arranged in a pump housing 14, which is sealed to the motor housing 3 and partially disposed in this and partially within the housing cover 4.
  • the shaft end 9 protrudes into a bearing bore 15 of larger diameter, which runs coaxially to the bearing bore 10 and in which a dipping into them pin 16 of the drive member 13 is rotatably mounted.
  • a driving coupling 17 is arranged between the shaft end 9 of the electric motor 2 and the journal 16 of the drive member 13, as they are in an enlarged scale in the FIGS. 3 and 4 is shown. Since both the shaft end 9 is mounted in the bottom bearing 11, as well as the drive member 13 with its journal 16, this driving coupling 17 is to cause a certain clearance compensation, both in the longitudinal and in the transverse direction.
  • the bottom bearing 11 is in fact designed as a fixed bearing and rigidly arranged between the machine housing 12, the pump housing 14, and the magnetic ring 6.
  • two pump rotors namely except the drive member 13, a driven part 18.
  • the drive member 13 is driven by the shaft end 9 of the electric motor 2 and the driving clutch 17 and transmits its rotational movement by toothed entrainment on the Output part 18.
  • cycloid gears are provided which have corresponding facing each other working surfaces. As a result, 12 pumping work spaces 19 are formed between these work surfaces and the inner wall of the machine housing, as in FIG. 2 shown.
  • FIGS. 3 and 4 it can be seen, the driving clutch 17, a ring member 20, with a hexagonal recess 21, in which a corresponding hexagonal shaped end portion of the shaft end 9 of the electric motor 2 is inserted for a desired turning and on the front side four plug-in pin 23 are arranged, which in corresponding end face on Running pin 16 arranged openings are inserted.
  • FIGS. 1 and 2 An end opening of the machine housing 12 is closed on the output side by a bottom bearing 22 which is arranged coaxially with the output part 18.
  • a bearing bore 24 is arranged, in which via a journal 25 of the output member 18 is mounted.
  • the drive member 13 and the output member 18 are loaded in the direction against each other by the hydraulic delivery pressure in which between the pump chamber pressure side and the opposite sides of the drive parts 13, 18 via holes or channels connection.
  • the output member 18 is supported with a spherical elevation 26 on a corresponding spherical recess 27 of the drive member 13 from.
  • the pump housing 14 may, as in FIGS. 1 and 2 represented, in particular cases pot-shaped, with a corresponding obliquely to the drive axis, but at right angles to the axis of the driven part 18, extending bottom 28 on which the bottom bearing 22 of the driven part 18 rests and is supported.
  • an additional structural decoupling of the pump side is advantageously given by the drive side, which can be particularly important in service.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Drehkolbenmaschine nach der Gattung des Hauptanspruches. Eine solche Drehkolbenmaschine mit stirnseitiger Verzahnung eines Antriebsteils und eines Abtriebsteils und zwischen den Zähnen sich befindlichen Arbeitsräumen, die sich während des Rotierens vergrößern und verkleinern, wodurch die Förderwirkung des Mediums erzeugt wird, ist mehrfach schon vorgeschlagen worden. Bei einem solchen älteren Vorschlag ( DE 103 35 939 A1 ) sind zur Verringerung von Spaltverlusten zwischen den Rotoren diese in axialer und radialer Richtung frei verschiebbar, wobei derartige Spaltverluste sowohl Fertigungsbedingt sein können aber auch Folge von Erschütterungen einer solchen Drehkolbenmaschine während des Betriebs und dadurch gegebenes ungewünschtes Ändern der Lage der Rotoren in ihrer Anordnung. Insofern ist auch der dort vorgeschlagene zusätzliche Anpressdruck vom Druck des Fluidstromes her wenig hilfreich.The invention relates to a rotary piston engine according to the preamble of the main claim. Such a rotary engine with frontal toothing of a drive part and a driven part and located between the teeth workrooms that enlarge and reduce during rotation, whereby the conveying effect of the medium is generated, has already been proposed several times. In such an older proposal ( DE 103 35 939 A1 ) are to reduce gap losses between the rotors in the axial and radial directions freely displaced, such gap losses may be both manufacturing but also result of shocks such a rotary piston machine during operation and thereby given unwanted changing the position of the rotors in their arrangement. In this respect, the additional contact pressure proposed there is also of little help from the pressure of the fluid flow.

Bei einem anderen die Gattung des Hauptanspruchs betreffenden Vorschlag ( WO 2005/024236 A1 ) sind die Rotoren sowohl als der Läufer des Elektromotors auf einer feststehenden Achse angeordnet, was natürlich auf Kosten der Justierbarkeit geht, so dass auch das Anordnen in einer Grundeinstellung nicht möglich ist. Nicht zuletzt ist auch nur das Antriebsteil der Rotoren axial auf der Achse verschiebbar, was natürlich auch die Einstellmöglichkeit entsprechend einschränkt.In another proposal concerning the type of the main claim ( WO 2005/024236 A1 ) The rotors are both arranged as the rotor of the electric motor on a fixed axis, which of course is at the expense of adjustability, so that the arrangement in a basic setting is not possible. Not least, only the drive part of the rotors is axially displaceable on the axis, which of course also limits the adjustment accordingly.

Bei wieder einem anderen Vorschlag an einer gattungsgemäßen Pumpe ( WO 2005/024237 A1 ) ist das Abtriebsteil in Richtung Antriebsteil belastet, um dadurch die für den Einsatz als Zuführpumpe von Benzineinspritzanlagen gewünschte Baueinheit zwischen Motorgehäuse und Maschinengehäuse zu erzielen. Durch eine in Richtung des Antriebsteils vorgesehene Belastung des Abtriebsteils kann zwar das axiale Spiel verringert werden aber eine Grundeinstellung oder eine entsprechende Flexibilität zum Justieren der Pumpe ist nicht gegeben.In another proposal on a generic pump ( WO 2005/024237 A1 ), the output member is loaded in the direction of the drive part, thereby to achieve the desired for use as a feed pump of gasoline injection engine assembly between the motor housing and the machine housing. Although provided in the direction of the drive part load of the driven part, although the axial clearance can be reduced but a basic setting or a corresponding flexibility for adjusting the pump is not given.

Bei einer gattungsgemäßen Drehkolbenmaschine ( WO 2005/116403 A1 ) ist zusätzlich vorgeschlagen worden, über Gleitlager der Rotoren diese axial verschieben zu können, um dadurch auch die gewünschte Leistung der Maschine zu ändern. Außerdem geht es bei dieser Maschine nicht um Bodenlager sondern um spezielle Gleitlager der Rotoren.In a generic rotary piston engine ( WO 2005/116403 A1 ) has been proposed in addition to be able to move axially about plain bearings of the rotors, thereby also changing the desired performance of the machine. In addition, this machine is not about floor bearings but special bearings of the rotors.

Bei einer anderen elektrisch angetriebenen Pumpe ( US PS 5145348 ) handelt es sich um eine Innenzahnradpumpe die sowohl von dem erzielbaren Wirkungsgrad als auch in Bezug auf die der Antriebskraft entsprechenden Leistung von der gattungsgemäßen Maschine stark abweicht.For another electrically driven pump ( US PS 5145348 ) is an internal gear pump which deviates greatly from both the achievable efficiency and with respect to the power corresponding to the power of the generic machine.

Bei einer anderen bekannten elektrisch angetriebenen Pumpe ( US PS 5425625 ) handelt es sich ebenfalls um eine Innenzahnradpumpe mit völlig anderem Aufbau als der der gattungsgemäßen Pumpe.In another known electrically driven pump ( US PS 5425625 ) It is also an internal gear pump with a completely different structure than that of the generic pump.

Zugrundeliegende AufgabeUnderlying task

Der Erfindung liegt die Aufgabe zugrunde eine Drehkolbenmaschine der gattungsgemäßen Art so zu verbessern, dass sie besonders günstig herstellbar ist, eine Grundeinstellung ermöglicht und ein Festklemmen der Rotoren auch bei Erschüttungen im Betrieb vermieden wird.The invention has for its object to improve a rotary piston engine of the generic type so that it is particularly inexpensive to produce, allows a basic setting and a clamping of the rotors is avoided even when shaken during operation.

Die Erfindung und ihre VorteileThe invention and its advantages

Die erfindungsgemäße Drehkolbenmaschine wird durch den Hauptanspruch definiert.The rotary piston engine according to the invention is defined by the main claim.

Die Erfindung weist dafür die in der zugrundeliegenden Aufgabe genannten Vorteile auf. Je nach Art der Festlegung der Bodenlager in Kombination damit, dass Antriebsteil und Abtriebsteil innerhalb des Maschinengehäuses angeordnet und durch die Bodenlager eingeschlossen sind, kann einerseits eine nachträgliche Justierung des Spiels vorgenommen werden, bis hin zu einer Grundeinstellung, und es kann andererseits ein nachträgliches ungewünschtes Festklemmen der Laufteile unterbunden werden, auch weil eine Baueinheit zwischen Bodenlager und Maschinengehäuse besteht. Es verbleibt also ein erforderliches axiales Spiel.The invention has the advantages mentioned in the underlying task. Depending on the type of fixing the floor bearing combined with it, that drive part and output part within arranged on the machine housing and enclosed by the floor bearings, on the one hand a subsequent adjustment of the game can be made, up to a basic setting, and on the other hand, a subsequent undesired clamping of the running parts can be prevented, also because a unit between the bottom bearing and machine housing. So there remains a required axial clearance.

Nach einer vorteilhaften Ausgestaltung der Erfindung weist für einen günstigen Lauf der Rotoren das Antriebsteil und/oder Abtriebsteil auf der dem Pumpenraum abgewandten Seite einen Laufzapfen auf, und das Bodenlager weist eine ringförmig ausgebildete zentrale Lagerbohrung zur Aufnahme des Laufzapfens auf.According to an advantageous embodiment of the invention, for a favorable running of the rotors, the drive part and / or driven part on the side facing away from the pump chamber on a journal, and the bottom bearing has a ring-shaped central bearing bore for receiving the journal.

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im folgenden näher beschrieben.An embodiment of the object of the invention is illustrated in the drawing and described in more detail below.

Es zeigen:

Fig. 1
eine Kraftstoffförderpumpe mit erfindungsgemäßer Drehkolbenmaschine im Längsschnitt entsprechend dem Pfeil I in Figur 2;
Fig. 2
einen Längsschnitt durch diese Förderpumpe entsprechend der Linie II-II in Figur 1
Fig. 3
eine Mitnahmekupplung der Förderpumpe im Längsschnitt und in vergrößertem Maßstab und
Fig. 4
die Axialansicht dieser Mitnahmekupplung entsprechend dem Pfeil III in Figur 3.
Show it:
Fig. 1
a fuel pump with inventive rotary piston machine in longitudinal section according to the arrow I in FIG. 2 ;
Fig. 2
a longitudinal section through this pump according to the line II-II in FIG. 1
Fig. 3
a driving coupling of the pump in longitudinal section and on an enlarged scale and
Fig. 4
the axial view of this driving coupling according to the arrow III in FIG. 3 ,

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die dargestellte Kraftstoffförderpumpe weist eine Drehkolbenpumpe 1 und einen diese antreibenden Elektromotor 2 auf, welche in einem Motorgehäuse 3 und einem daran befestigten Gehäusedeckel 4 angeordnet sind. Hierbei ist besonders der Elektromotor stark vereinfacht dargestellt mit einem Läufer 5 und einem Magnetring 6, sowie einem axialen Verschlussteil 7 des Motorgehäuses 3, welches mit diesem verbunden und zu diesem hin abgedichtet ist. Außerdem ist an diesem Verschlussteil 7 eine Drehlagerung 8 des Läufers 5 vorgesehen. Vorzugsweise ist der Elektromotor 5, 6 zu dessen Kühlung vom Kraftstoff innerhalb des Motorgehäuses 3 umströmt.The fuel delivery pump shown has a rotary piston pump 1 and an electric motor 2 driving this, which are arranged in a motor housing 3 and a housing cover 4 attached thereto. Here, in particular, the electric motor is shown greatly simplified with a rotor 5 and a magnetic ring 6, and an axial closure part 7 of the motor housing 3, which is connected thereto and sealed to this. In addition, a rotary bearing 8 of the rotor 5 is provided on this closure part 7. Preferably, the electric motor 5, 6 flows around its cooling by the fuel within the motor housing 3.

Das zweite Drehlager des Läufers 5 ist an seinem Wellenende 9 in einer Lagerbohrung 10 eines Bodenlagers 11 vorgesehen, welches in eine entsprechende Öffnung an der Stirnseite eines Maschinengehäuses 12 der Drehkolbenpumpe 1 angeordnet ist und an dem sich ein stirnseitig verzahntes Antriebsteil 13 der Pumpe auf der dem Motor zugewandten Seiten axial abstützen kann. Dieses Maschinengehäuse 12 ist in einem Pumpengehäuse 14 angeordnet, das zum Motorgehäuse 3 hin abgedichtet und teilweise in diesem und teilweise innerhalb des Gehäusedeckels 4 angeordnet ist. Das Wellenende 9 ragt in eine Lagerbohrung 15 größeren Durchmessers, welche koaxial zur Lagerbohrung 10 verläuft und in welcher ein in sie tauchender Laufzapfen 16 des Antriebsteils 13 drehbar gelagert ist.The second pivot bearing of the rotor 5 is provided at its shaft end 9 in a bearing bore 10 of a bottom bearing 11, which is arranged in a corresponding opening on the end face of a machine housing 12 of the rotary lobe pump 1 and on which a frontally toothed drive part 13 of the pump on the Can axially support motor facing sides. This machine housing 12 is arranged in a pump housing 14, which is sealed to the motor housing 3 and partially disposed in this and partially within the housing cover 4. The shaft end 9 protrudes into a bearing bore 15 of larger diameter, which runs coaxially to the bearing bore 10 and in which a dipping into them pin 16 of the drive member 13 is rotatably mounted.

In der Lagerbohrung 15 ist zwischen dem Wellenende 9 des Elektromotors 2 und dem Laufzapfen 16 des Antriebsteils 13 eine Mitnahmekupplung 17 angeordnet, wie sie in vergrößertem Maßstab in den Figuren 3 und 4 dargestellt ist. Da sowohl das Wellenende 9 im Bodenlager 11 gelagert ist, als auch das Antriebsteil 13 mit seinem Laufzapfen 16, soll diese Mitnahmekupplung 17 einen gewissen Spielausgleich bewirken und zwar sowohl in Längs- als auch in Querrichtung. Das Bodenlager 11 ist nämlich als Festlager ausgebildet und zwischen dem Maschinengehäuse 12, dem Pumpengehäuse 14, bzw. dem Magnetring 6 starr angeordnet.In the bearing bore 15, a driving coupling 17 is arranged between the shaft end 9 of the electric motor 2 and the journal 16 of the drive member 13, as they are in an enlarged scale in the FIGS. 3 and 4 is shown. Since both the shaft end 9 is mounted in the bottom bearing 11, as well as the drive member 13 with its journal 16, this driving coupling 17 is to cause a certain clearance compensation, both in the longitudinal and in the transverse direction. The bottom bearing 11 is in fact designed as a fixed bearing and rigidly arranged between the machine housing 12, the pump housing 14, and the magnetic ring 6.

In dem Maschinengehäuse 12 arbeiten zwei Pumprotoren, nämlich außer dem Antriebsteil 13 ein Abtriebsteil 18. Das Antriebsteil 13 wird durch das Wellenende 9 des Elektromotors 2 und die Mitnahmekupplung 17 angetrieben und überträgt seine Drehbewegung durch zahnschlüssige Mitnahme auf das Abtriebsteil 18. Auf den Stirnseiten des Antriebsteils 13 und des Abtriebsteils 18 sind hierfür zykloide Verzahnungen vorgesehen, die entsprechende einander zugewandte Arbeitsflächen aufweisen. Hierdurch werden zwischen diesen Arbeitsflächen und der Innenwand des Maschinengehäuses 12 Pumparbeitsräume 19 gebildet, wie in Figur 2 gezeigt.In the machine housing 12, two pump rotors, namely except the drive member 13, a driven part 18. The drive member 13 is driven by the shaft end 9 of the electric motor 2 and the driving clutch 17 and transmits its rotational movement by toothed entrainment on the Output part 18. On the front sides of the drive part 13 and the output part 18 for this purpose cycloid gears are provided which have corresponding facing each other working surfaces. As a result, 12 pumping work spaces 19 are formed between these work surfaces and the inner wall of the machine housing, as in FIG. 2 shown.

Wie aus Figur 3 und 4 ersichtlich weist die Mitnahmekupplung 17 ein Ringteil 20 auf, mit einer sechseckigen Innenausnehmung 21, in welche ein entsprechend sechseckig gestalteter Endabschnitt des Wellenendes 9 des Elektromotors 2 für eine gewünschte Drehschlüssigkeit gesteckt wird und an dem stirnseitig vier Steckzapfen 23 angeordnet sind, welche in entsprechende stirnseitig am Laufzapfen 16 angeordnete Öffnungen gesteckt sind.How out FIGS. 3 and 4 it can be seen, the driving clutch 17, a ring member 20, with a hexagonal recess 21, in which a corresponding hexagonal shaped end portion of the shaft end 9 of the electric motor 2 is inserted for a desired turning and on the front side four plug-in pin 23 are arranged, which in corresponding end face on Running pin 16 arranged openings are inserted.

Eine Stirnseitenöffnung des Maschinengehäuses 12 ist abtriebsseitig durch ein Bodenlager 22 verschlossen, welches gleichachsig zum Abtriebsteil 18 angeordnet ist. In diesem Bodenlager 22 ist eine Lagerbohrung 24 angeordnet, in welcher über einen Laufzapfen 25 des Abtriebsteils 18 dieses gelagert ist. Wie aus Figur 1 und 2 nicht erkennbar ist, werden zudem das Antriebsteil 13 und das Abtriebsteil 18 in Richtung gegeneinander durch den hydraulischen Förderdruck belastet, in dem zwischen dem Pumpenraum druckseitig und den einander abgewandten Seiten der Triebteile 13, 18 über Bohrungen oder Kanäle eine Verbindung besteht. Hierbei stützt sich das Abtriebsteil 18 mit einer sphärischen Erhebung 26 an einer entsprechenden sphärischen Ausnehmung 27 des Antriebsteils 13 ab.An end opening of the machine housing 12 is closed on the output side by a bottom bearing 22 which is arranged coaxially with the output part 18. In this bottom bearing 22, a bearing bore 24 is arranged, in which via a journal 25 of the output member 18 is mounted. How out FIGS. 1 and 2 can not be seen, also the drive member 13 and the output member 18 are loaded in the direction against each other by the hydraulic delivery pressure in which between the pump chamber pressure side and the opposite sides of the drive parts 13, 18 via holes or channels connection. In this case, the output member 18 is supported with a spherical elevation 26 on a corresponding spherical recess 27 of the drive member 13 from.

Das Pumpengehäuse 14 kann, wie in Figur 1 und 2 dargestellt, in besonderen Fällen topfförmig ausgebildet sein, mit einem entsprechend schräg zur Antriebsachse, jedoch im rechten Winkel zur Achse des Abtriebsteils 18, verlaufenden Boden 28, auf dem das Bodenlager 22 des Abtriebsteils 18 aufliegt und sich abstützt. Hierdurch ist vorteilhafterweise eine zusätzliche konstruktive Abkopplung der Pumpenseite von der Antriebsseite gegeben, was besonders beim Service von Bedeutung sein kann.The pump housing 14 may, as in FIGS. 1 and 2 represented, in particular cases pot-shaped, with a corresponding obliquely to the drive axis, but at right angles to the axis of the driven part 18, extending bottom 28 on which the bottom bearing 22 of the driven part 18 rests and is supported. As a result, an additional structural decoupling of the pump side is advantageously given by the drive side, which can be particularly important in service.

BezugszahlenlisteLIST OF REFERENCE NUMBERS

11 DrehkolbenpumpeRotary pump 22 Elektromotorelectric motor 33 Motorgehäusemotor housing 44 Gehäusedeckelhousing cover 55 Läuferrunner 66 Magnetringmagnetic ring 77 Verschlussteilclosing part 88th Drehlagerungpivot bearing 99 Wellenendeshaft end 1010 Lagerbohrungbearing bore 1111 Bodenlagerbottom support 1212 Maschinengehäusemachine housing 1313 Antriebsteildriving part 1414 Pumpengehäusepump housing 1515 Lagerbohrungbearing bore 1616 Laufzapfen (von 13)Journal (from 13) 1717 Mitnahmekupplungdriving coupling 1818 Abtriebsteilstripping section 1919 PumparbeitsräumePump workrooms 2020 Ringteilring part 2121 Innenausnehmunginner recess 2222 Bodenlagerbottom support 2323 Steckzapfenplug-in pin 2424 Lagerbohrungbearing bore 2525 Laufzapfenrunning pins 2626 Erhebung an 18Collection at 18 2727 Ausnehmung an 13Recess at 13 2828 Bodenground

Claims (2)

  1. Rotary piston machine (1)
    - with at least two rotors which cooperate by virtue of a driving part (13) and a driven part (18) and which delimit working spaces (19) by end-face toothing and the respective axes of rotation of which form a specific angle with one another,
    - with a machine housing (12) receiving the driving part (13) and the driven part (18),
    - with a suction duct and a delivery duct which are connectable intermittently to the working spaces (19) during the running of the rotors, and
    - with an electric motor, arranged in a motor housing (3), for the drive (2) of the driving part (13),
    - the machine housing (12) and the motor housing (3) being connected to one another,
    - with a play-possessing rotary mounting (11, 22) of the driving part (13) and the driven part (18) with respect to the machine housing (12) and/or in the direction of the other part,
    - the driving part (13) and/or the driven part (18) being mounted with play in the direction of the other part,
    - the driving part (13) and/or the driven part (18) for the rotary mounting being arranged in a bottom bearing (11, 22) which determines their or its axial angular position and allows axial play and which is connected to the machine housing (12) to form a structural unit,
    characterized in that
    the bottom bearing (11, 22), in order to be secured in the machine housing (12), is screwed, glued or pressed with its radial marginal region into a corresponding end-face orifice of the machine housing (12), the machine housing (12), designed as a unit, being introduced into a pump housing (14) which is closed on the end face facing away from the electric motor (2), and the pump housing (14) being of pot-shaped design with a bottom (28), running obliquely with respect to its mid-axis, for supporting the bottom bearing (22) of the driven part (18).
  2. Rotary piston machine according to Claim 1, characterized in that the driving part (13) and/or the driven part (18) have/has a running journal (16, 25) on the side facing away from the pumping space (19), and in that the bottom bearing (11, 22), designed in the form of a ring, has a central bearing bore (15, 24) for receiving the running journal (16, 25).
EP06722634.0A 2005-03-16 2006-03-16 Rotary piston machine Active EP1859170B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005012511 2005-03-16
PCT/DE2006/000478 WO2006097092A1 (en) 2005-03-16 2006-03-16 Rotary piston machine

Publications (2)

Publication Number Publication Date
EP1859170A1 EP1859170A1 (en) 2007-11-28
EP1859170B1 true EP1859170B1 (en) 2013-05-15

Family

ID=36617303

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06722634.0A Active EP1859170B1 (en) 2005-03-16 2006-03-16 Rotary piston machine

Country Status (4)

Country Link
US (1) US7699592B2 (en)
EP (1) EP1859170B1 (en)
JP (1) JP5085528B2 (en)
WO (1) WO2006097092A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004026048A1 (en) * 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Gap leakage current control
US8834140B2 (en) * 2004-05-25 2014-09-16 Cor Pumps + Compressors Ag Leakage loss flow control and associated media flow delivery assembly
JP5840337B2 (en) 2007-07-05 2016-01-06 ハーレー−ダビッドソン・モーター・カンパニー・グループ・エルエルシー Wheel speed sensor
DE502008002903D1 (en) * 2007-08-31 2011-04-28 Bosch Gmbh Robert AIR MOTOR
US8539931B1 (en) 2009-06-29 2013-09-24 Yousry Kamel Hanna Rotary internal combustion diesel engine
US9115646B2 (en) * 2010-06-17 2015-08-25 Exponential Technologies, Inc. Shroud for rotary engine
JP6084435B2 (en) * 2012-08-08 2017-02-22 Ntn株式会社 Internal gear pump
EP4053411A4 (en) * 2019-11-01 2023-11-15 Shenzhen Spherical Fluid Power Technology Co., Ltd Spherical pump rotor static pressure support and spherical pump provided with static pressure support
DE102020206493A1 (en) * 2020-05-25 2021-11-25 Hyundai Motor Company Fuel pump for a liquid fuel injection system of a motor vehicle

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US324246A (en) * 1885-08-11 John flelding
US739207A (en) * 1902-05-28 1903-09-15 Jens Nielsen Rotary pump.
US2016605A (en) * 1932-02-24 1935-10-08 James L Kempthorne Pump, compressor, and the like
US2040178A (en) * 1933-11-11 1936-05-12 James L Kempthorne Pump or the like
US2501998A (en) * 1938-02-21 1950-03-28 Dutrey Andre Roto-volumetric pump
US2375923A (en) * 1940-08-02 1945-05-15 Johnson Otto William Pump
US3040664A (en) * 1959-04-13 1962-06-26 Flo Motive Corp Dual cavity fluid handling device
US3101700A (en) * 1960-06-14 1963-08-27 Meredith E Bowdish Rotary compressor or engine
US3816039A (en) * 1971-08-02 1974-06-11 Commercial Metals Co Rotary air pump with rotating and oscillating center piston
JPS59105081U (en) * 1982-12-30 1984-07-14 いすゞ自動車株式会社 gear pump
US5145348A (en) * 1991-05-15 1992-09-08 Eaton Corporation Gerotor pump having an improved drive mechanism
US5425625A (en) * 1994-03-24 1995-06-20 Lenco Enterprises Co., Ltd. Car-used electric fuel pump
US6739852B1 (en) * 1995-03-09 2004-05-25 Outland Technologies Usa, Inc. Rotary engine and method for determining engagement surface contours therefor
US6497564B2 (en) * 2000-01-07 2002-12-24 James B. Klassen Balanced rotors positive displacement engine and pump method and apparatus
US7318712B2 (en) * 2002-08-02 2008-01-15 Cor Pumps + Compressors Ag Rotary piston machines comprising a displaceable inner housing
US7390181B2 (en) * 2003-09-11 2008-06-24 Cor Pumps + Compressors Ag Rotating piston machine
DE502004002805D1 (en) * 2003-09-11 2007-03-15 Cor Pumps & Compressors Ag ROTARY MACHINE
DE102004026048A1 (en) * 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Gap leakage current control

Also Published As

Publication number Publication date
JP2008537579A (en) 2008-09-18
EP1859170A1 (en) 2007-11-28
US7699592B2 (en) 2010-04-20
JP5085528B2 (en) 2012-11-28
US20080219876A1 (en) 2008-09-11
WO2006097092A1 (en) 2006-09-21

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