EP2137378B1 - Pump or motor - Google Patents

Pump or motor Download PDF

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Publication number
EP2137378B1
EP2137378B1 EP08734365.3A EP08734365A EP2137378B1 EP 2137378 B1 EP2137378 B1 EP 2137378B1 EP 08734365 A EP08734365 A EP 08734365A EP 2137378 B1 EP2137378 B1 EP 2137378B1
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EP
European Patent Office
Prior art keywords
working
shaft
working part
pump
motor according
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Active
Application number
EP08734365.3A
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German (de)
French (fr)
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EP2137378A1 (en
Inventor
Felix Arnold
Evgenij Skrynski
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Priority to SI200831911T priority Critical patent/SI2137378T1/en
Publication of EP2137378A1 publication Critical patent/EP2137378A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F01C3/085—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 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed valves
    • 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
    • F04C2240/60—Shafts

Definitions

  • the invention relates to a pump or a motor for liquid or gaseous media according to the preamble of the main claim.
  • a known machine of this type DE OS 42 41 320
  • the working part wherein according to a machine with spur toothing, the working spaces between the work surfaces to promote the medium reduced, or increased.
  • a machine with spur toothing the working spaces between the work surfaces to promote the medium reduced, or increased.
  • such a machine can also serve as a motor by medium is pumped into the work spaces under pressure, which generates a drive of the shaft by enlarging the work spaces.
  • two working parts are rotated in the machine housing with correspondingly high demands on the pivot bearing and thrust bearing and with a significant performance limitation in terms of working pressure.
  • the invention has for its object a pump or a motor for liquid or gaseous media, namely to develop a related machine, with the much higher working pressures of the media without disadvantage are acceptable and can be produced without a considerable manufacturing effort.
  • the erimdungsdorfe machine with the characterizing features of the main claims 1 and 2 has the advantage that with a simple structure and correspondingly low cost, a machine for high working pressures is created in the advantageously in the known machines by radial load adversely affecting pressures now predominantly in the be redirected easily controllable axial direction. Due to the stationary arrangement of the other working part opposite the working surface delimiting working surface, bearing forces of a second working part also fall away, so that only the working part has a bearing surface towards the shaft on the oblique sliding plane and predominantly only the shaft has an axial bearing and only a small extent Radial storage must have. The rotation of the shaft corresponds to the tumbling of the working part.
  • the central axis of the stationary working surface is equal to the axis of rotation of the shaft.
  • the partially tumbling inner wall receiving the tumbling working part merges into a cylindrical opening of the housing, the diameter of which corresponds to the diameter of the working part.
  • the central axis of the stationary working surface is arranged coaxially to the shaft, on the one hand results in a favorable Auflagerung the working part on the static work surface, but also a working space separating large teilkugelige overlap area between the working part and the housing.
  • the teeth of the oppositely arranged spur toothing are formed as a cycloid toothing with power and Absperrteil with a cycloidal development of the tread.
  • a cycloid toothing with power and Absperrteil with a cycloidal development of the tread is known ( DE 42 41 320 ), but in an embodiment in which the opposing work surfaces rotate in each case.
  • the advantages of cycloidal processing are retained if only as in the invention, a work surface rotates. The advantages of cycloidal processing as such can be seen in the prior art.
  • valves plate valves serve as valves plate valves with an outer and an inner ring having holding part and arranged between the rings, attached to one of the rings resilient valve plates.
  • Such plate valves are extremely inexpensive to produce and work in the manner of a check valve.
  • material tapers are present at the bearing point between the inclined plane of the working part and the shaft in the medium through the connection channel, so as to compensate for the resulting in the formation of the inclined plane without mass balance resulting unilateral mass accumulation by material rejuvenation. This avoids that one-sided mass accumulations in the region of the inclined plane on the shaft creates unilateral radial forces.
  • FIG. 1 an embodiment of the invention is shown in longitudinal section, as it then in Fig. 3 is shown in perspective view.
  • This is a machine that can be used depending on the application as a pump or motor for liquid or gaseous media, and how, especially Fig. 3 removed, the cross section of the mounting housing 1 is cylindrical in order to use the machine in corresponding holes can.
  • round cord rings 2 form the required seal of the mounting housing 1, to which the machine receiving part, such as a pipe but also a hole in a machine receiving this machine.
  • a shaft 4 is rotatably supported via a radial bearing 3, wherein the shaft is slightly loaded in the axial direction via a leaf spring 5 and a locking ring 6 and is correspondingly displaceable.
  • a non-co-rotating working space housing 10 is arranged coaxially with the shaft 4 centrally and sealed by a O-ring 11 to the installation housing 1 out.
  • This working space housing 10 accommodates a working space 12, which is bounded on the other hand by a rotating working part 13.
  • the shaft 4 has on the side facing the working part 13 an inclined sliding plane 14, so that a rotation of the shaft 4 leads to a tumbling of the working part 13.
  • the glide plane 14 facing away from the end face of the working part 13 is toothed in the manner of a cycloid toothing, which engages in accordance with existing in a working housing 10 static teeth in the opposite wall surface of the working space 12.
  • the working part 13 is guided in spherical boundaries of the receiving working space housing 10, namely in a part spherical surface portion 15 which also forms the outer boundary of the working spaces 12 radially and a central smaller part spherical surface portion 16, the work spaces 12 radially limited to the inside.
  • Both partial spherical surface sections 15 and 16 have the same center point M.
  • the working part 13 also has on its side facing the surface 16 a corresponding partial spherical surface 17, as well as a larger diameter 15 of the partial spherical surface section Due to this spherical overlap not only is there a very favorable distribution of the axial forces of the shaft 4 on the working space housing 10, but there is also a very favorable separation of the working space to working space or working space to other machine channels and this particular during the Operation, ie the tumbling of the working part 13.
  • the working space housing 10 is fastened via a screw ring 19 in the installation housing 1, wherein a valve plate 20 is clamped between the screw ring 19 and the working space housing 10.
  • a valve plate 20 is clamped between the screw ring 19 and the working space housing 10.
  • connection channels 21 are arranged for the working medium centrally symmetrical about an axis X of the machine, leading to the work spaces 12.
  • the axis X is at the same time the axis of rotation of the shaft 4 and passes through the center M of the spherical surfaces accordingly.
  • annular space 23 To the working spaces 12 there is a connection via control channels 22 to a shaft surrounding the annular space 23 for the working fluid, the annular space 23 depending on the application serves as inflow or outflow channel.
  • this annular space 23 communicates via radial channels 24 with an outer annular space 25 in connection, as particularly Fig. 3 is removable. When installing the machine such an annular space 25 is then brought into coincidence with at least one channel for the medium.
  • first variant of the embodiment has only a pin 26 on the working part, which is inserted into a bore 27 of the shaft, said pin coaxially runs to the axis of the working part.
  • the machine is the same structure as that in the Fig. 1 to 3 Shown.
  • the Fig. 5 to 7 show the control in the region of the inclined sliding plane 14 according to the embodiment Fig. 1 , wherein the working part 13 of the working spaces 12 has channels 28 which open into the sliding plane 14. These channels 28 interact with the control channels 22 on the in Fig. 7 shown front side of the shaft 4 to the inclined sliding plane 14 together.
  • the shaft 4 has on the oblique sliding plane 14 side facing a larger diameter than on its stored portion, so that the control channels 22 can be arranged in the step thus formed and corresponding to the control of the channels 28 in the inclined sliding plane 14 are opposite to this ,
  • the diameter R1 and R2 on the channels 28 receiving boundary circles almost the same diameter as that of the spherical surface portions 15 and 16th
  • Fig. 13 can be removed, would be due to the inclined sliding plane 14, the mass accumulation at the top of the shaft 4 and in particular in the control area on one side, so that one-sided radial forces would arise.
  • a recess 32 is provided in the control region of the head, so that a mass balance and thus unilateral radial forces are thereby avoided again.
  • Due to a remaining radial portion 33 of the inclined sliding plane is avoided that the over flowing in the bottom of the working part 13 and there provided openings 22 medium enters undesirable areas, especially between the head of the shaft 4 and the working space housing 10.
  • channels 28 for the connection of the Bottom of the working part 13 arranged channels 28 ( Fig.

Landscapes

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

Description

Stand der Technik und dessen NachteileState of the art and its disadvantages

Die Erfindung geht aus von einer Pumpe oder einem Motor für flüssige oder gasförmige Medien nach der Gattung des Hauptanspruchs. Bei einer bekannten Maschine dieser Art ( DE OS 42 41 320 ) wird über die Welle das Arbeitsteil angetrieben, wobei entsprechend einer Maschine mit Stirnverzahnung die Arbeitsräume zwischen den Arbeitsflächen zur Förderung des Mediums verkleinert, bzw. vergrößert werden. Umgekehrt kann eine solche Maschine auch als Motor dienen, indem in die Arbeitsräume unter Druck Medium gefördert wird, das dabei durch Vergrößerung der Arbeitsräume einen Antrieb der Welle erzeugt. In jedem Fall werden zwei Arbeitsteile im Maschinengehäuse rotierend bewegt mit entsprechend hohen Anforderungen an die Drehlagerung sowie auch Axiallagerung und mit einer erheblichen Leistungsbegrenzung in Bezug auf den Arbeitsdruck.The invention relates to a pump or a motor for liquid or gaseous media according to the preamble of the main claim. In a known machine of this type ( DE OS 42 41 320 ) is driven via the shaft, the working part, wherein according to a machine with spur toothing, the working spaces between the work surfaces to promote the medium reduced, or increased. Conversely, such a machine can also serve as a motor by medium is pumped into the work spaces under pressure, which generates a drive of the shaft by enlarging the work spaces. In any case, two working parts are rotated in the machine housing with correspondingly high demands on the pivot bearing and thrust bearing and with a significant performance limitation in terms of working pressure.

Bei einer anderen bekannten Maschine dieser Art ( US PS 3,236,186 ) sind die beiden stirnseitig mit ihren Zähnen ineinander greifenden Teile in einem Gehäuse mit kugeligem Innenraum angeordnet, wobei im Zentrum eine kugelige Ausgestaltung an den Teilen die beim Rotierende entstehende Taumelbewegung der Teile zueinander ermöglicht. Auch hier besteht eine entsprechend hohe Anforderung an die Drehlagerung der Teile sowie deren Axiallagerung, so dass vor allem der Höhe des Arbeitsdrucks enge Grenzen gesetzt sind. Außerdem ist der Aufwand für die Herstellung derartiger konvex, bzw. konkav ausgebildeter Flankenflächen an den Zähnen der Stirnverzahnung außerordentlich aufwendig.In another known machine of this type ( U.S. Patent 3,236,186 ) are the two frontally with their teeth interlocking parts arranged in a housing with spherical interior, wherein in the center of a spherical configuration of the parts allows the resulting rotational movement of the parts to each other. Again, there is a correspondingly high demand on the pivotal mounting of the parts and their axial bearing, so that in particular the height of the working pressure are set narrow limits. In addition, the cost of producing such convex, or concave flank surfaces on the teeth of the spur gear is extremely expensive.

In der US 3 895 610 ist eine andere bekannte Maschine dieser Art beschrieben.In the US 3,895,610 is another known machine of this type described.

Bei diesen bekannten Pumpen oder Motoren zweigen konstruktionsbedingt die Zu- und Abfluss zu den Arbeitsräumen bildenden Kanäle radial zu den Arbeitsteilen ab, so dass hierdurch ebenfalls eine dem Leistungsdruck entsprechende Radialbelastung der Arbeitsteile vorhanden ist. Abgesehen davon bewirkt die Strömung des Mediums über die radialen Kanten der die Mündungen der Kanäle steuernden Kanten an den Arbeitsteilen eine entsprechende Abnutzung, die mit entsprechender Zunahme des Leistungsverlusts mit deren Betriebsdauer der Maschine ebenfalls zunimmt. Durch diese Abnutzung auch auf der Kugelfläche der Zähne findet in diesem äußeren Kugelbereich derselben eine Undichtheit von einem Arbeitsraum zum nächsten statt, wobei die ansonsten vorteilhafte geringe Überlappung der radialen Stirnseite der Zähne zu der gegenüberliegenden Kugelwand sich besonders nachteilig auswirkt.In these known pumps or motors branches by design, the inflow and outflow to the working spaces forming channels radially from the working parts, so that in this way also a power pressure corresponding radial load of the working parts is present. Apart from this, the flow of the medium over the radial edges of the edges of the channels controlling the channels on the working parts causes a corresponding wear, which also increases with a corresponding increase in the power loss with the operating time of the machine. Due to this wear also on the spherical surface of the teeth, a leakage from one working space to the next takes place in this outer spherical region thereof, the otherwise advantageous slight overlap of the radial end face of the teeth to the opposite spherical wall having a particularly disadvantageous effect.

Der Erfindung zugrundeliegende AufgabeThe problem underlying the invention

Der Erfindung liegt die Aufgabe zugrunde eine Pumpe bzw. einen Motor für flüssige oder gasförmige Medien, nämlich eine diesbezügliche Maschine zu entwickeln, mit der auch wesentlich höhere Arbeitsdrücke der Medien ohne Nachteil verkraftbar sind und die ohne einen erheblichen Fertigungsaufwand herstellbar ist.The invention has for its object a pump or a motor for liquid or gaseous media, namely to develop a related machine, with the much higher working pressures of the media without disadvantage are acceptable and can be produced without a considerable manufacturing effort.

Die Erfindung und ihre VorteileThe invention and its advantages

Die erimdungsgemäße Maschine mit den kennzeichnenden Merkmalen der Hauptansprüche 1 und 2 hat den Vorteil, dass bei einfachem Aufbau und entsprechend geringen Kosten eine Maschine für hohe Arbeitsdrücke geschaffen wird, bei der vorteilhafterweise die bei den bekannten Maschinen sich durch Radialbelastung nachteilig auswirkenden Drücke nunmehr überwiegend in die leichter beherrschbare Axialrichtung umgeleitet werden. Durch das ortsfeste Anordnen der anderen dem Arbeitsteil gegenüberliegenden die Arbeitsräume begrenzenden Arbeitsfläche fallen auch Lagerkräfte eines zweiten Arbeitsteils weg, so dass lediglich das Arbeitsteil zur Welle hin auf der schiefen Gleitebene eine Lagerfläche aufweist und überwiegend nur die Welle eine Axiallagerung und nur in geringem Umfang auch eine Radiallagerung aufweisen muss. Dem Rotieren der Welle entspricht dabei das Taumeln des Arbeitsteils. Infolge dieses Taumelns werden die Arbeitsräume beim Rotieren der Welle nacheinander verkleinert, bzw. vergrößert, wodurch die entsprechende Leistung der Maschine entsteht. Bei den bekannten insbesondere Drehkolbenmaschinen wie der Wankelmaschine oder auch einer Exzenterschneckenpumpe wird meist in einer Schnittebene gedacht, was zu Schwierigkeiten in der Vorstellung der erfinderischen Gestaltung führt. Entscheidend für die Erfindung ist, dass die ortsfeste Arbeitsfläche und die Arbeitsfläche des taumelnden Arbeitsteils einen guten Formschluss auch zu den Kugelflächen aufweisen, wobei eine Flächenstetigkeit besteht mit während der Arbeit bleibender Dichtigkeit, also unabhängig von der Axiallage des Arbeitsteils.The erimdungsgemäße machine with the characterizing features of the main claims 1 and 2 has the advantage that with a simple structure and correspondingly low cost, a machine for high working pressures is created in the advantageously in the known machines by radial load adversely affecting pressures now predominantly in the be redirected easily controllable axial direction. Due to the stationary arrangement of the other working part opposite the working surface delimiting working surface, bearing forces of a second working part also fall away, so that only the working part has a bearing surface towards the shaft on the oblique sliding plane and predominantly only the shaft has an axial bearing and only a small extent Radial storage must have. The rotation of the shaft corresponds to the tumbling of the working part. As a result of this tumbling the work spaces are reduced in size when rotating the shaft successively, or increased, whereby the corresponding power of the machine is created. In the known in particular rotary piston engines such as the Wankelmaschine or a progressing cavity pump is usually in a sectional plane thought, which leads to difficulties in the idea of inventive design. Decisive for the invention is that the stationary working surface and the working surface of the tumbling working part have a good fit also to the spherical surfaces, wherein a surface continuity exists with permanent during work tightness, that is independent of the axial position of the working part.

Nach einer vorteilhaften Ausgestaltung der Erfindung ist die Mittelachse der ortsfesten Arbeitsfläche gleich der Drehachse der Welle. Hierdurch ist ein Optimum des Taumelantriebs erreichbar.According to an advantageous embodiment of the invention, the central axis of the stationary working surface is equal to the axis of rotation of the shaft. As a result, an optimum of the wobble drive can be achieved.

Nach einer zusätzlichen Ausgestaltung der Erfindung geht die das taumelnde Arbeitsteil aufnehmende teilkugelige Innenwand in eine zylindrische Öffnung des Gehäuses über, deren Durchmesser dem Durchmesser des Arbeitsteils entspricht. Insbesondere wenn die Mittelachse der ortsfesten Arbeitsfläche achsgleich zur Welle angeordnet ist, ergibt sich einerseits eine günstige Auflagerung des Arbeitsteils auf der statischen Arbeitsfläche, aber auch eine die Arbeitsräume trennende große teilkugelige Überlappungsfläche zwischen Arbeitsteil und Gehäuse.According to an additional embodiment of the invention, the partially tumbling inner wall receiving the tumbling working part merges into a cylindrical opening of the housing, the diameter of which corresponds to the diameter of the working part. In particular, when the central axis of the stationary working surface is arranged coaxially to the shaft, on the one hand results in a favorable Auflagerung the working part on the static work surface, but also a working space separating large teilkugelige overlap area between the working part and the housing.

Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung ist zwischen Arbeitsteil und gegenüberliegender, nicht mitrotierender Arbeitsfläche zentral eine gemeinsame teilkugelig ausgebildete Auflagefläche vorhanden, die ebenfalls zur radialen Begrenzung der Pumpenarbeitsräume dient. Auch hierdurch ist eine die Arbeitsräume trennende große Überlappung zwischen den kugeligen Auflageflächen gegeben mit entsprechenden Vorteilen für den Wirkungsgrad der Maschine.According to an additional advantageous embodiment of the invention is between the working part and opposite, not co-rotating work surface centrally a common teilkugelig formed support surface available, which also serves to radially limit the pump work spaces. Also, this is a working space separating large overlap between the spherical bearing surfaces given with corresponding advantages for the efficiency of the machine.

Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung sind die Zähne der einander gegenüberliegend angeordneten Stirnverzahnung als Zykloidenverzahnung ausgebildet mit Leistungsteil und Absperrteil mit einer zykloidischen Abwicklung der Lauffläche. An sich ist eine solche Ausgestaltung bekannt ( DE 42 41 320 ), allerdings in einer Ausgestaltung, bei der die einander gegenüberliegenden Arbeitsflächen jeweils mitrotieren. Die Vorteile der zykloidischen Abwicklung bleiben jedoch erhalten, wenn nur, wie bei der Erfindung, eine Arbeitsfläche rotiert. Die Vorteile der zykloidischen Abwicklung als solche sind dem Stand der Technik entnehmbar.According to an additional advantageous embodiment of the invention, the teeth of the oppositely arranged spur toothing are formed as a cycloid toothing with power and Absperrteil with a cycloidal development of the tread. As such, such an embodiment is known ( DE 42 41 320 ), but in an embodiment in which the opposing work surfaces rotate in each case. However, the advantages of cycloidal processing are retained if only as in the invention, a work surface rotates. The advantages of cycloidal processing as such can be seen in the prior art.

Nach einer zusätzlichen in Anspruch 11 auch für sich geltend gemachten Ausgestaltung der Erfindung zweigen Zu- und/oder Abflüsse aus den Arbeitsräumen als statische Kanäle von der ortsfesten Arbeitsfläche achssymmetrisch und vom Arbeitsteil ungesteuert ab. Hierdurch wird eine scharfe Steuerkante zwischen dem taumelnden Arbeitsteil und einer kugeligen Wand vermieden mit entsprechender Qualitätsverschlechterung bei an sich unvermeidbarer Abnutzung der Steuerkanten. Allerdings ist für manche Funktionssysteme eine zusätzliche Ventilsteuerung gewünscht, weshalb nach einer diesbezüglichen zusätzlichen Ausgestaltung der Erfindung in den statischen Kanälen steuerbare Ventile angeordnet sein können.According to an additional claimed in claim 11 embodiment of the invention inflows and / or outflows from the work spaces as static channels of the stationary work surface axisymmetric and uncontrolled from the working part. As a result, a sharp control edge between the tumbling working part and a spherical wall is avoided with a corresponding deterioration in quality at inevitable wear of the control edges. However, an additional valve control is desired for some functional systems, which is why controllable valves can be arranged in the static channels according to an additional embodiment of the invention.

Nach einer zusätzlichen diesbezüglichen vorteilhaften Ausgestaltung der Erfindung dienen als Ventile Plattenventile mit einem einen äußeren und einen inneren Ring aufweisenden Halteteil und mit zwischen den Ringen angeordneten, an einem der Ringe befestigten federnden Ventilplatten. Derartige Plattenventile sind äußerst günstig herstellbar und arbeiten in Art eines Rückschlagventils.According to an additional relevant advantageous embodiment of the invention serve as valves plate valves with an outer and an inner ring having holding part and arranged between the rings, attached to one of the rings resilient valve plates. Such plate valves are extremely inexpensive to produce and work in the manner of a check valve.

Nach einer zusätzlichen diesbezüglichen Ausgestaltung der Erfindung sind an der Auflagerstelle zwischen der schiefen Ebene des Arbeitsteils und der Welle im Bereich der Mediumsdurchleitung zum Verbindungskanal hin Materialverjüngungen vorhanden, um damit die sich bei der Bildung der schiefen Ebene ohne Massenausgleich ergebende einseitige Massenanhäufung durch Materialverjüngungen auszugleichen. Hierdurch wird vermieden, dass durch einseitige Massenanhäufungen im Bereich der schiefen Ebene an der Welle einseitige Radialkräfte entstehen.After an additional relevant embodiment of the invention, material tapers are present at the bearing point between the inclined plane of the working part and the shaft in the medium through the connection channel, so as to compensate for the resulting in the formation of the inclined plane without mass balance resulting unilateral mass accumulation by material rejuvenation. This avoids that one-sided mass accumulations in the region of the inclined plane on the shaft creates unilateral radial forces.

Zusätzliche Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind in der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Additional advantages and advantageous embodiments of the invention will become apparent in the following description, the drawings and the claims.

Ein Ausführungsbeispiel mit Variante ist in der Zeichnung dargestellt und im folgenden näher beschrieben.An embodiment with variant is shown in the drawing and described in more detail below.

Zeichnungdrawing

Es zeigen:

Fig. 1
einen Längsschnitt gemäß der Schnittlinie A-A aus Fig. 2 einer Pumpe oder einem Motor für flüssig oder gasförmige Medien,
Fig. 2
eine Ansicht der Maschine aus Fig. 1 gemäß dem Pfeil B,
Fig. 3
eine perspektivische Ansicht der Maschine,
Fig. 4
einen Längsschnitt der Maschine entsprechend Fig. 1 mit einer ersten Variante des Arbeitsteils,
Fig. 5
einen Längsschnitt durch ein Arbeitsteil entsprechend dem Schnitt C-C in Fig. 6,
Fig. 6
eine Ansicht entsprechend dem Pfeil D in Fig. 5,
Fig. 7
eine Draufsicht auf die der Ansicht D gegenüberliegenden Steuerfläche der Welle,
Fig. 8
einen Längsschnitt durch das Pumpengehäuse entsprechend der Linie E-E in Fig. 9,
Fig. 9
eine Ansicht des Pumpengehäuses aus Fig. 8 entsprechend dem Pfeil F,
Fig. 10
eine Draufsicht auf eine Ventilplatte,
Fig. 11
die Ventilplatte aus Fig. 10 in perspektivischer Ansicht,
Fig. 12
eine zweite Variante des Ausführungsbeispiels und
Fig. 13
die Welle aus dieser Variante in perspektivischer Ansicht.
Show it:
Fig. 1
a longitudinal section according to the section line AA Fig. 2 a pump or motor for liquid or gaseous media,
Fig. 2
a view of the machine Fig. 1 according to the arrow B,
Fig. 3
a perspective view of the machine,
Fig. 4
a longitudinal section of the machine accordingly Fig. 1 with a first variant of the working part,
Fig. 5
a longitudinal section through a working part corresponding to the section CC in Fig. 6 .
Fig. 6
a view corresponding to the arrow D in Fig. 5 .
Fig. 7
a top view of the opposite of the view D control surface of the shaft,
Fig. 8
a longitudinal section through the pump housing according to the line EE in Fig. 9 .
Fig. 9
a view of the pump housing Fig. 8 according to the arrow F,
Fig. 10
a plan view of a valve plate,
Fig. 11
the valve plate off Fig. 10 in perspective view,
Fig. 12
a second variant of the embodiment and
Fig. 13
the wave from this variant in perspective view.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Fig. 1 ist ein Ausführungsbeispiel der Erfindung im Längsschnitt dargestellt, wie es dann auch in Fig. 3 in perspektivischer Ansicht gezeigt ist. Hierbei handelt es sich um eine Maschine, die je nach Einsatz als Pumpe oder Motor für flüssige oder gasförmige Medien einsetzbar ist, wobei, wie besonders Fig. 3 entnehmbar, der Querschnitt des Einbaugehäuses 1 zylindrisch ist, um die Maschine in entsprechende Bohrungen einsetzen zu können. Zur nicht dargestellten Bohrungswand hin bilden Rundschnurringe 2 die erforderliche Abdichtung des Einbaugehäuses 1, zu dem die Maschine aufnehmenden Teil, wie beispielsweise einer Rohrleitung aber auch einer Bohrung in einer diese Maschine aufnehmenden Vorrichtung. In diesem Einbaugehäuse 1 ist über ein Radiallager 3 eine Welle 4 drehbar gelagert, wobei über eine Blattfederung 5 und einen Sicherungsring 6 die Welle in axialer Richtung leicht belastet und entsprechend verschiebbar ist. Zur Dichtung dient ein Rundschnurring 7 zwischen Welle 4 und einem Gehäuseeinsatz 8, der sich über ein Axiallager 9 am Einbaugehäuse 1 abstützt und an dem die Blattfederung 5 angreift. Während des Rotierens der Welle 4 wird auch aus Reibungsgründen der Gehäuseeinsatz 8 mit Blattfederung 5 und Rundschnurring 7 mitgenommen, wobei der Gehäuseeinsatz 8 auf seiner dem Axiallager 9 abgewandten Stirnseite ein Labyrinth als Dichtung aufweist, welches teilweise in entsprechende Ausnehmungen des Einbaugehäuses greift.In Fig. 1 an embodiment of the invention is shown in longitudinal section, as it then in Fig. 3 is shown in perspective view. This is a machine that can be used depending on the application as a pump or motor for liquid or gaseous media, and how, especially Fig. 3 removed, the cross section of the mounting housing 1 is cylindrical in order to use the machine in corresponding holes can. To the bore wall, not shown, round cord rings 2 form the required seal of the mounting housing 1, to which the machine receiving part, such as a pipe but also a hole in a machine receiving this machine. In this installation housing 1, a shaft 4 is rotatably supported via a radial bearing 3, wherein the shaft is slightly loaded in the axial direction via a leaf spring 5 and a locking ring 6 and is correspondingly displaceable. To seal a round cord ring 7 between shaft 4 and a housing insert 8, which is supported via a thrust bearing 9 on the mounting housing 1 and on which the leaf spring 5 acts. During rotation of the shaft 4, the housing insert 8 is entrained with leaf spring 5 and O-ring 7 for reasons of friction, wherein the housing insert 8 on its side facing away from the thrust bearing 9 has a labyrinth seal, which partially engages in corresponding recesses of the mounting housing.

Im Einbaugehäuse 1 ist achsgleich mit der Welle 4 ein nicht mitrotierendes Arbeitsraumgehäuse 10 zentral angeordnet und über einen Rundschnurring 11 zum Einbaugehäuse 1 hin abgedichtet. Dieses Arbeitsraumgehäuse 10 nimmt einen Arbeitsraum 12 auf, der andererseits durch ein rotierendes Arbeitsteil 13 begrenzt wird. Die Welle 4 weist auf der dem Arbeitsteil 13 zugewandten Seite eine schiefe Gleitebene 14 auf, so dass ein Rotieren der Welle 4 zu einem Taumeln des Arbeitsteils 13 führt. Die der Gleitebene 14 abgewandte Stirnseite des Arbeitsteils 13 ist verzahnt in Art einer Zykloidenverzahnung, die entsprechend in eine am Arbeitsgehäuse 10 vorhandene statische Verzahnung in der gegenüberliegenden Wandfläche des Arbeitsraums 12 greift. Beim Rotieren des Arbeitsteils 13 innerhalb dieses ortsfest angeordneten Arbeitsraumgehäuses 10 vergrößern, bzw. verkleinern sich die Arbeitsräume 12, was zu der gewünschten Pump-, bzw. Motorwirkung führt. Hierbei berühren sich zur jeweiligen Pumpenraumbegrenzung die einander zugeordneten Zähne vom Arbeitsteil 13 und dem Arbeitsraumgehäuse 10 linienförmig.In the installation housing 1, a non-co-rotating working space housing 10 is arranged coaxially with the shaft 4 centrally and sealed by a O-ring 11 to the installation housing 1 out. This working space housing 10 accommodates a working space 12, which is bounded on the other hand by a rotating working part 13. The shaft 4 has on the side facing the working part 13 an inclined sliding plane 14, so that a rotation of the shaft 4 leads to a tumbling of the working part 13. The glide plane 14 facing away from the end face of the working part 13 is toothed in the manner of a cycloid toothing, which engages in accordance with existing in a working housing 10 static teeth in the opposite wall surface of the working space 12. When rotating the working part 13 within this fixedly arranged working space housing 10 enlarge or reduce the working space 12, which leads to the desired pump, or motor effect. In this case, the mutually associated teeth of the working part 13 and the working space housing 10 are linearly in contact with the respective pump space boundary.

Um eine Führung bei der Taumelbewegung zu erzielen ist das Arbeitsteil 13 in kugeligen Begrenzungen des es aufnehmenden Arbeitsraumgehäuses 10 geführt, nämlich in einem Teilkugelflächenabschnitt 15, der auch radial die äußere Begrenzung der Arbeitsräume 12 bildet und einem zentralen kleineren Teilkugelflächenabschnitt 16, der die Arbeitsräume 12 radial nach innen begrenzt. Beide Teilkugelflächenabschnitte 15 und 16 haben den gleichen Mittelpunkt M. Das Arbeitsteil 13 weist auf seiner der Fläche 16 zugewandten Seite ebenfalls eine entsprechende Teilkugelrundung 17 auf, sowie eine dem Teilkugelflächenabschnitt größeren Durchmessers 15 entsprechende Teilkugelrundung 18. Aufgrund dieser kugeligen Überlappung besteht nicht nur eine sehr günstige Verteilung der Axialkräfte von der Welle 4 auf das Arbeitsraumgehäuse 10, sondern es besteht auch eine äußerst günstige Trennung von Arbeitsraum zu Arbeitsraum bzw. von Arbeitsraum zu sonstigen Maschinenkanälen und dies insbesondere während des Betriebs, d. h. des Taumelns des Arbeitsteils 13.In order to achieve a guide in the tumbling movement, the working part 13 is guided in spherical boundaries of the receiving working space housing 10, namely in a part spherical surface portion 15 which also forms the outer boundary of the working spaces 12 radially and a central smaller part spherical surface portion 16, the work spaces 12 radially limited to the inside. Both partial spherical surface sections 15 and 16 have the same center point M. The working part 13 also has on its side facing the surface 16 a corresponding partial spherical surface 17, as well as a larger diameter 15 of the partial spherical surface section Due to this spherical overlap not only is there a very favorable distribution of the axial forces of the shaft 4 on the working space housing 10, but there is also a very favorable separation of the working space to working space or working space to other machine channels and this particular during the Operation, ie the tumbling of the working part 13.

Das Arbeitsraumgehäuse 10 ist über einen Schraubring 19 im Einbaugehäuse 1 befestigt, wobei zwischen Schraubring 19 und Arbeitsraumgehäuse 10 eine Ventilplatte 20 eingespannt ist. Bei der in Fig. 2 dargestellten Ansicht B ist gezeigt, wie in dieser Ventilplatte 20 Anschlusskanäle 21 für das Arbeitsmedium zentralsymmetrisch um eine Achse X der Maschine angeordnet sind, die zu den Arbeitsräumen 12 führen. Die Achse X ist gleichzeitig die Drehachse der Welle 4 und geht entsprechend durch den Mittelpunkt M der Kugelflächen.The working space housing 10 is fastened via a screw ring 19 in the installation housing 1, wherein a valve plate 20 is clamped between the screw ring 19 and the working space housing 10. At the in Fig. 2 shown view B is shown as in this valve plate 20 connection channels 21 are arranged for the working medium centrally symmetrical about an axis X of the machine, leading to the work spaces 12. The axis X is at the same time the axis of rotation of the shaft 4 and passes through the center M of the spherical surfaces accordingly.

Zu den Arbeitsräumen 12 besteht eine Verbindung über Steuerkanäle 22 zu einem die Welle umgebenden Ringraum 23 für das Arbeitsmedium, wobei der Ringraum 23 je nach Einsatz als Zu- oder Abflusskanal dient. Bei dem dargestellten Ausführungsbeispiel steht dieser Ringraum 23 über Radialkanäle 24 mit einem äußeren Ringraum 25 in Verbindung, wie besonders Fig. 3 entnehmbar ist. Beim Einbau der Maschine wird ein solcher Ringraum 25 dann in Überdeckung mit mindestens einem Kanal für das Medium gebracht.To the working spaces 12 there is a connection via control channels 22 to a shaft surrounding the annular space 23 for the working fluid, the annular space 23 depending on the application serves as inflow or outflow channel. In the illustrated embodiment, this annular space 23 communicates via radial channels 24 with an outer annular space 25 in connection, as particularly Fig. 3 is removable. When installing the machine such an annular space 25 is then brought into coincidence with at least one channel for the medium.

Die in Fig. 4 dargestellte erste Variante des Ausführungsbeispiels weist lediglich einen Zapfen 26 am Arbeitsteil auf, der in eine Bohrung 27 der Welle gesteckt ist, wobei dieser Zapfen achsgleich zur Achse des Arbeitsteils verläuft. Im übrigen ist die Maschine genauso aufgebaut wie die in den Fig. 1 bis 3 Dargestellte.In the Fig. 4 shown first variant of the embodiment has only a pin 26 on the working part, which is inserted into a bore 27 of the shaft, said pin coaxially runs to the axis of the working part. Moreover, the machine is the same structure as that in the Fig. 1 to 3 Shown.

Die Fig. 5 bis 7 zeigen die Steuerung im Bereich der schiefen Gleitebene 14 nach dem Ausführungsbeispiel aus Fig. 1, wobei das Arbeitsteil 13 von den Arbeitsräumen 12 her Kanäle 28 aufweist, die in die Gleitebene 14 münden. Diese Kanäle 28 wirken mit den Steuerkanälen 22 auf der in Fig. 7 gezeigten Stirnseite der Welle 4 zur schiefen Gleitebene 14 hin zusammen. Die Welle 4 weist auf der der schiefen Gleitebene 14 zugewandten Seite einen größeren Durchmesser auf als auf ihrem gelagerten Abschnitt, so dass die Steuerkanäle 22 in der dadurch gebildeten Stufe angeordnet werden können und entsprechend zur Steuerung der Kanäle 28 in der schiefen Gleitebene 14 diesen gegenüber liegen. Wie in Fig. 6 gezeigt sind die Durchmesser R1 und R2 auf den die Kanäle 28 aufnehmenden Begrenzungskreisen nahezu die gleichen Durchmesser wie die der Kugelflächenabschnitte 15 und 16.The Fig. 5 to 7 show the control in the region of the inclined sliding plane 14 according to the embodiment Fig. 1 , wherein the working part 13 of the working spaces 12 has channels 28 which open into the sliding plane 14. These channels 28 interact with the control channels 22 on the in Fig. 7 shown front side of the shaft 4 to the inclined sliding plane 14 together. The shaft 4 has on the oblique sliding plane 14 side facing a larger diameter than on its stored portion, so that the control channels 22 can be arranged in the step thus formed and corresponding to the control of the channels 28 in the inclined sliding plane 14 are opposite to this , As in Fig. 6 Shown are the diameter R1 and R2 on the channels 28 receiving boundary circles almost the same diameter as that of the spherical surface portions 15 and 16th

In den Fig. 8 bis 11 ist die Leitung des Mediums von oder zu den Arbeitsräumen 12 im Arbeitsraumgehäuse 10 gezeigt. Die Anschlusskanäle 21, die zu den Arbeitsräumen 12 hin- bzw. wegführen, sind durch die Ventilplatte 20 abgedeckt, auf der wiederum ein Ventilring 29 mit Federplatten 30 angeordnet ist, die die Anschlusskanäle 21 in Art eines Rückschlagventils steuern.In the 8 to 11 the conduit of the medium from or to the working spaces 12 in the working space housing 10 is shown. The connecting channels 21, which lead to the working spaces 12 and lead away, are covered by the valve plate 20, on which in turn a valve ring 29 is arranged with spring plates 30 which control the connection channels 21 in the manner of a check valve.

Bei der in den Fig. 12 und 13 gezeigten zweiten Variante sind, soweit sie sich entsprechen, die Bezugszahlen aus den Fig. 1 bis 11 übernommen und werden wie folgt ergänzt. In dieser Variante wird vor allem angestrebt irgendwelche an der Welle 4 angreifende Radialkräfte zu unterbinden. Aus diesem Grund wird die Leitung des Fördermediums statt radial abzuführen zentral durch die Welle geleitet und zwar durch einen dort vorgesehenen Verbindungskanal 31. Hierfür ist achsgleich mit der Achse X eine entsprechende Bohrung in der Welle 4 vorgesehen, die kopfseitig mit den Arbeitsräumen 12 und zwar über die schiefe Gleitebene 14 verbunden ist und die andererseits vorteilhafterweise die nunmehr als Spiralfeder ausgebildete Feder 5 aufnehmen kann, die zudem in einfacher Art im Vordruck verstellbar ist.In the in the FIGS. 12 and 13 shown second variant, as far as they correspond, the reference numbers from the Fig. 1 to 11 and are supplemented as follows. In this variant, the aim is above all to prevent any radial forces acting on the shaft 4. For this reason, the line of the fluid instead of radially dissipate centrally through the shaft For this purpose, a corresponding bore in the shaft 4 is provided coaxially with the axis X, which is connected on the head side with the work spaces 12 and that on the inclined sliding plane 14 and the other advantageously formed now as a spiral spring Can accommodate spring 5, which is also adjustable in a simple manner in the form.

Wie der Fig. 13 entnehmbar ist, wäre in Folge der schiefen Gleitebene 14 die Massenanhäufung am Kopf der Welle 4 und insbesondere im Steuerbereich einseitig, so dass auch einseitige Radialkräfte entstehen würden. Erfindungsgemäß ist deshalb im Steuerbereich des Kopfes eine Ausnehmung 32 vorgesehen, so dass dadurch wieder ein Massenausgleich und damit einseitige Radialkräfte vermieden werden. Aufgrund eines verbleibenden Radialabschnittes 33 der schiefen Gleitebene wird vermieden, dass das über im Boden des Arbeitsteils 13 und dort vorgesehene Öffnungen 22 strömende Medium in ungewünschte Bereiche gelangt, vor allem zwischen den Kopf der Welle 4 und das Arbeitsraumgehäuse 10. Natürlich kann zur Verbindung der im Boden des Arbeitsteils 13 angeordneten Kanälen 28 (Fig. 5) zu der schiefen Gleitebene hin entweder im Arbeitsteil 13 oder in der ihm zugewandten schiefen Gleitebene 14 der Welle 4 eine radial außen vorhandene und eine Ausnehmung für das strömende Medium bewirkende Vertiefung vorgesehen sein. Bezugszahlenliste 1 Einbaugehäuse 31 Verbindungskanal 2 Rundschnurring 32 Ausnehmung 3 Radiallager 33 Radialabschnitt 4 Welle 5 Blattfederung 6 Sicherungsring 7 Rundschnurring 8 Gehäuseeinsatz 9 Axiallager 10 Arbeitsraumgehäuse 11 Rundschnurring 12 Arbeitsraum 13 Arbeitsteil 14 schiefe Gleitebene 15 Teilkugelflächenabschnitt 16 Teilkugelflächenabschnitt 17 Teilkugelrundung 18 Teilkugelrundung 19 Schraubring 20 Ventilplatte 21 Anschlusskanäle 22 Steuerkanäle 23 Ringraum 24 Radialkanäle 25 äußerer Ringraum 26 Zapfen 27 Bohrung 28 Kanäle 29 Ventilring 30 Federplatte Again Fig. 13 can be removed, would be due to the inclined sliding plane 14, the mass accumulation at the top of the shaft 4 and in particular in the control area on one side, so that one-sided radial forces would arise. According to the invention, therefore, a recess 32 is provided in the control region of the head, so that a mass balance and thus unilateral radial forces are thereby avoided again. Due to a remaining radial portion 33 of the inclined sliding plane is avoided that the over flowing in the bottom of the working part 13 and there provided openings 22 medium enters undesirable areas, especially between the head of the shaft 4 and the working space housing 10. Of course, for the connection of the Bottom of the working part 13 arranged channels 28 ( Fig. 5 ) to the inclined sliding plane either in the working part 13 or in the inclined inclined plane 14 facing the shaft 4 there may be provided a radially outer recess and a recess for the flowing medium causing depression. LIST OF REFERENCE NUMBERS 1 installation housing 31 connecting channel 2 O-ring 32 recess 3 radial bearings 33 radial section 4 wave 5 Steel suspension 6 circlip 7 O-ring 8th housing insert 9 thrust 10 Working space housing 11 O-ring 12 working space 13 working part 14 inclined slip plane 15 Partial spherical surface section 16 Partial spherical surface section 17 Partial sphere rounding 18 Partial sphere rounding 19 screw ring 20 valve plate 21 connecting channels 22 control channels 23 annulus 24 radial channels 25 outer annulus 26 spigot 27 drilling 28 channels 29 valve ring 30 spring plate

Claims (15)

  1. Pump or motor for liquid or gaseous media
    - having working spaces which are arranged between working faces which lie opposite one another and are symmetrical with respect to their respective rotational axes,
    - having in each case one spur toothing system on the two working faces, the teeth of which spur toothing systems, which are assigned to one another, delimit the working spaces (12) by way of contact lines which run radially and engage into one another,
    - having a defined corresponding angle between the respective axes of the two working surfaces,
    - having a working part (13) which can be rotated about its axis and has a spur toothing system for receiving one of the working faces,
    - having a spherical radial boundary of the working part (13) or the working faces for sealing mounting on a partially spherical inner wall of a housing (10),
    - having a radial boundary of the working spaces by way of that partially spherical inner wall of the housing which engages around the working part and on which the working part is mounted such that it can tumble about its axis and seals radially on the walls,
    - having a rotating drive or output via a shaft (4), and
    - having in each case one inflow and one outflow to the ducts (21, 22) which form working spaces (12) for the medium,
    - an oblique sliding plane (14) being arranged between the shaft (4) and the working part (13) which is provided with a spur toothing system and a working face, with the result that rotating of the shaft (4) leads to tumbling of the working part (13), or tumbling of the working part (13) leads to rotating of the shaft (4), and
    - with the result that the other working face (on 10) which lies opposite the working part (13), with a spur toothing system which corresponds to the spur toothing system of the working part (13), is arranged so as to not corotate and therefore in a stationary manner in the housing (10),
    characterized in that,
    towards the oblique sliding plane (14), the shaft (4) has a diameter which is increased in relation to its mounted section, and, in order to forward the liquid or gaseous media, the shaft (4) has a connecting duct (31) which runs in the shaft (4) and is connected via the oblique sliding plane (14) and openings (28) in the working part (13) to the working spaces (12).
  2. Pump or motor for liquid or gaseous media
    - having working spaces which are arranged between working faces which lie opposite one another and are symmetrical with respect to their respective rotational axes,
    - having in each case one spur toothing system on the two working faces, the teeth of which spur toothing systems, which are assigned to one another, delimit the working spaces (12) by way of contact lines which run radially and engage into one another,
    - having a defined corresponding angle between the respective axes of the two working surfaces,
    - having a working part (13) which can be rotated about its axis and has a spur toothing system for receiving one of the working faces,
    - having a spherical radial boundary of the working part (13) or the working faces for sealing mounting on a partially spherical inner wall of a housing (10),
    - having a radial boundary of the working spaces by way of that partially spherical inner wall of the housing which engages around the working part and on which the working part is mounted such that it can tumble about its axis and seals radially on the walls,
    - having a rotating drive or output via a shaft (4), and
    - having in each case one inflow and one outflow to the ducts (21, 22) which form working spaces (12) for the medium,
    - an oblique sliding plane (14) being arranged between the shaft (4) and the working part (13) which is provided with a spur toothing system and a working face, with the result that rotating of the shaft (4) leads to tumbling of the working part (13), or tumbling of the working part (13) leads to rotating of the shaft (4), and
    - with the result that the other working face (on 10) which lies opposite the working part (13), with a spur toothing system which corresponds to the spur toothing system of the working part (13), is arranged so as to not corotate and therefore in a stationary manner in the housing (10),
    characterized in that,
    towards the oblique sliding plane (14), the shaft (4) has a diameter which is increased in relation to its mounted section, and in that corotating ducts (22) which serve as an inflow or outflow run in the step which is formed as a result, and in that there are openings (28) which correspond to the ducts (22) in the working face of the working part (13), and the said openings (28) are controlled by the mouths of the ducts (22) in the oblique sliding plane (14).
  3. Pump or motor according to Claim 1 or 2, characterized in that the centre axis (X) of the stationary working face is identical to the rotational axis of the shaft (4).
  4. Pump or motor according to one of the preceding claims, characterized in that the partially spherical inner wall (15) which receives the tumbling working part (13) merges into a cylindrical opening of the housing (10), the diameter of which cylindrical opening corresponds to the diameter of the working part (13).
  5. Pump or motor according to one of the preceding claims, characterized in that the machine has cylindrical external dimensions for the installation into bores or pipelines.
  6. Pump or motor according to one of the preceding Claims 2 to 5, characterized in that a pin (26) is arranged on the oblique sliding plane (14) between the working part (13) and the shaft (4), which pin (26) engages into a corresponding guide bore (27) of the opposite part (working part or shaft) (Fig. 4).
  7. Pump or motor according to Claim 6, characterized in that the pin (26) is arranged on the working part (13).
  8. Pump or motor according to one of the preceding claims, characterized in that the shaft (4) including the working part (13) is loaded flexibly (5) in the direction of the stationary working face, and in that the shaft is mounted in an overall housing such that it can be rotated and displaced axially.
  9. Pump or motor according to one of the preceding claims, characterized in that there is a common spherically configured supporting face (16) centrally between the working part (13) and the working face which lies opposite and does not corotate, which supporting face (16) likewise serves to radially delimit the pump working spaces (12).
  10. Pump or motor according to one of the preceding claims, characterized in that the teeth of the spur toothing systems which are arranged so as to lie opposite one another are configured as a cycloid toothing system, with a power part and a shut-off part with a cycloidal development of the running face.
  11. Pump or motor according to one of the preceding claims, characterized in that inlets and/or outlets to/from the pump working spaces (12) branch off as static ducts (21) in an axially symmetrical manner from the stationary working face and in an uncontrolled manner from the working part (13).
  12. Pump or motor according to Claim 11, characterized in that the static ducts (21) can be controlled by valves (29, 30) which are arranged in the working space housing (10).
  13. Pump or motor according to Claim 12, characterized in that plate valves serve as valves, having a holding part which has an outer and an inner ring (29), and, arranged between the rings, spring plates (30) which are fastened in a sprung manner to one ring thereof.
  14. Pump or motor according to Claim 1, characterized in that there are openings (ducts 28 in Figs 5 and 6) on the bottom of the working spaces, which openings lead to a collecting space (32) which is present between the oblique sliding plane (14) and the rear side of the working part (13), the collecting space (32) being closed radially to the outside and leading directly to the connecting duct (31).
  15. Pump or motor according to Claim 1, characterized in that there are tapered material portions for mass balancing with regard to rotating forces at the supporting point between the working part (13) and the oblique sliding plane (14) of the shaft (4) in the region of the medium passage towards the connecting duct (31).
EP08734365.3A 2007-03-13 2008-03-13 Pump or motor Active EP2137378B1 (en)

Priority Applications (1)

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SI200831911T SI2137378T1 (en) 2007-03-13 2008-03-13 Pump or motor

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DE102007012574 2007-03-13
DE102008009694 2008-02-18
PCT/DE2008/000425 WO2008110155A1 (en) 2007-03-13 2008-03-13 Pump or motor

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EP (1) EP2137378B1 (en)
JP (1) JP5135361B2 (en)
CN (1) CN101960089B (en)
AU (1) AU2008226194B2 (en)
DE (1) DE102008013991A1 (en)
RU (1) RU2494261C2 (en)
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JP2010520964A (en) 2010-06-17
US20100104462A1 (en) 2010-04-29
CN101960089A (en) 2011-01-26
US8821142B2 (en) 2014-09-02
RU2494261C2 (en) 2013-09-27
AU2008226194A1 (en) 2008-09-18
WO2008110155A1 (en) 2008-09-18
US20130224056A1 (en) 2013-08-29
RU2009137617A (en) 2011-04-20
DE102008013991A1 (en) 2008-12-04
EP2137378A1 (en) 2009-12-30
JP5135361B2 (en) 2013-02-06
CN101960089B (en) 2013-07-31
SI2137378T1 (en) 2018-02-28
AU2008226194B2 (en) 2013-07-18

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