WO1996021108A1 - Pump for conveying a medium - Google Patents

Pump for conveying a medium Download PDF

Info

Publication number
WO1996021108A1
WO1996021108A1 PCT/EP1996/000015 EP9600015W WO9621108A1 WO 1996021108 A1 WO1996021108 A1 WO 1996021108A1 EP 9600015 W EP9600015 W EP 9600015W WO 9621108 A1 WO9621108 A1 WO 9621108A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
pump according
displacer
hollow shaft
pump
Prior art date
Application number
PCT/EP1996/000015
Other languages
German (de)
French (fr)
Inventor
Peter B. Kathmann
Original Assignee
Linear Anstalt
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19504366A external-priority patent/DE19504366C1/en
Application filed by Linear Anstalt filed Critical Linear Anstalt
Priority to EP96900298A priority Critical patent/EP0813654A1/en
Priority to JP8520731A priority patent/JPH11502277A/en
Priority to AU43904/96A priority patent/AU4390496A/en
Publication of WO1996021108A1 publication Critical patent/WO1996021108A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • F04B1/1072—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks with cylinder blocks and actuating cams rotating together

Definitions

  • the present invention relates to a pump for conveying a medium, in particular a gas-liquid mixture, according to the preamble of claim 1.
  • the radial piston pumps have a cylinder block that is eccentrically located in a housing. Pistons are arranged radially in the cylinder block and perform a lifting movement when the cylinder block rotates. The pistons are supported by rollers in the housing. The cylinder block is driven by a drive shaft which penetrates the housing and is connected to an external motor.
  • Radial piston pumps of this type have the disadvantage that their construction, in particular the piston guide in the cylinder block, is relatively complex.
  • pumps of this type cause problems in the production of gas-liquid mixtures, which occur in particular in the production of crude oil.
  • the object of the present invention is therefore to provide a pump which has a simple and compact structure and can be used to request gas-liquid mixtures.
  • two shafts inserted into one another are used, which are mounted independently of one another and eccentrically to one another in a housing.
  • the inner shaft has radially displaceable displacers, which are preferably guided in a radial bore in the circumferential surface of the inner shaft and form a displacement chamber together with the drilling base.
  • this displacer is advantageously pressed onto the inner peripheral surface of the outer shaft. Because of the eccentric arrangement of the inner shaft, the distance between the bottom of the borehole and the inner circumferential surface of the outer shaft changes continuously during one revolution, so that the displacer is displaced radially and thus the volume of the displacer chamber changes continuously.
  • the inner shaft is not driven directly, but indirectly via the outer shaft, which preferably has the armature windings of an electric motor.
  • the ones on the inner circumferential surface of the outer shaft which is also the rotor of the electric motor, serve as drivers for the inner shaft, the displacers being in frictional engagement with the rotor in an advantageous development. This allows the eccentric inner shaft to be driven with extremely little effort.
  • the media are preferably fed to the inner shaft at one shaft end and discharged at the other shaft end, so that the flow through the inner shaft is essentially linear.
  • the pump can thus be easily inserted into a line.
  • a plurality of displacers distributed over the circumferential surface are provided in order to increase the delivery rate in a simple manner.
  • Figure 1 is a schematic representation of a pump according to the invention in longitudinal section.
  • Figure 2 schematically shows a single displacer in longitudinal section.
  • the pump 1 shown in FIG. 1 consists of a pump housing 3, which can be cylindrical, for example.
  • the two long sides of the pump housing 3 are sealed off by means of a screw-on cover 5.
  • a complete electric motor is accommodated in the pump housing 3, only the stator winding 7 and the armature or rotor winding 9 being shown schematically in FIG. 1 for the sake of clarity.
  • the other necessary components of such an electric motor preferably a direct current motor, are known to the person skilled in the art and will therefore not be described in more detail here.
  • the armature winding 9 is formed in the circumferential surface of a shaft 11, which is referred to below only as a rotor.
  • the rotor 11 is in a corresponding bore in each cover 5 by means of a bearing, preferably a ball bearing, rotatably supported. The rotor 11 is thus rotatable about a longitudinal axis 17.
  • a further shaft 19 is arranged within the rotor 9, the outer diameter of the shaft 19 being smaller than the inner diameter of the rotor 11.
  • the rotatable mounting of the shaft 19 is also carried out via bores 21 provided in the two covers 5, the diameter of which is smaller than that of the bores 13 and which, viewed towards the outside of the cover, bores against the bores 13 conclude.
  • the rotatable support of the shaft 19 is ensured by bearings 23.
  • the two bores 13 and 21 are not coaxial to one another, but are formed eccentrically, the longitudinal axis 17 of the bore 13 being offset by an amount v from the longitudinal axis 25 of the bores 21.
  • Radially aligned recesses preferably bores 31, are made in the peripheral surface 27 of the shaft 19. These holes 31 are in turn connected via channels 33 to a channel 35 passing through the shaft 19 in the longitudinal direction.
  • FIG. 2 An enlarged illustration of such a bore 31 is shown in FIG. 2.
  • a displacer 37 which can be displaced in the radial direction is guided in the bore. This displacer has a cup shape, the open end 38 facing the bottom 39 of the bore 31.
  • the outer diameter of the displacer is only slightly smaller than the inner diameter of the bore 31.
  • the preferably dome-shaped closed end of the displacer 37 is supported on the inner peripheral surface 29 of the rotor 11.
  • a point-shaped extension 43 is preferably formed in the center of the spherical end, which thus serves as a contact point to the peripheral surface 29.
  • the displacer 37 is supported on the bottom of the borehole 39 by means of a spring 45, which extends to the closed end of the displacer 37.
  • the spring has the task of firmly pressing the displacer 37 against the inner circumferential surface 29.
  • the interior of the displacer 37 forms, together with the borehole section underneath, a displacement chamber 47, the volume of which depends on the distance d between the outer peripheral surface 27 and the inner peripheral surface 29.
  • the distance d between the outer circumferential surface 27 and the inner circumferential surface 29 changes continuously by an amount 2v during one revolution of the shaft 19. Since the displacer 37 is constantly pressed against the inner circumferential surface 29 by the spring 45, the previously mentioned change in distance leads to a stroke movement of the displacer 37 in the bore 31 by an amount 2v. The lifting movement in turn leads to a change in the volume of the displacement chamber 47. This effect is used for pumping a medium, liquid being sucked into the displacement chamber 27 via the channel 33 and the liquid again being reduced when the volume of the space is subsequently reduced is expelled.
  • the shaft 19 is driven by the rotor 11, in which the displacers 37 which are in frictional engagement with the inner peripheral surface 29 transmit the rotary movement to the shaft 19.
  • a suitable choice of the closed end 41 of the displacer 37 and the corresponding design of the spring 45 prevent the peripheral surface 29 from sliding over the displacer 37.
  • the displacers not only function normally, but also as carriers or Wise torque transmitters are used, ie no additional connecting parts between the rotor 11 and shaft 19 are necessary, a very simple and compact construction is possible.
  • the medium to be pumped passes through an opening 51 in the cover 5 into the channel 35 of the shaft 19.
  • the rotation of the shaft 19 also causes the medium in the channel 35 to rotate, with a demixing Liquid and gas are generated by the centrifugal force.
  • the heavier medium for example petroleum, collects in the area of the wall of the channel 35, while the gaseous medium collects in a central area.
  • the medium is sucked through the channel 33 into the displacer chamber 47 and in the subsequent ejection phase is pressed again through the channel 33 into the channel 35.
  • check valves 53 are provided in the channel 35, only shown schematically. The ejected medium then flows further through the channel 35 in the direction of a further opening 55 in the cover 5 opposite the opening 51, as is indicated by arrows in the figure.
  • the channel 35 is divided into two chambers 59 by means of a partition 57, the upper chamber with the upper row of displacement chambers and the lower chamber correspondingly with the lower row of Displacement chambers are connected.
  • the medium expelled from the upper displacer cannot get into the displacement chamber of the lower aspirating displacer.
  • the pump capacity of the pump shown in FIG. 1 can be increased further by increasing the number of displacers.
  • the present pump can be used for the most varied fields of application and pressure ranges.
  • the pump described above can also be used as a motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The present invention concerns a pump for conveying a medium, in particular a gas-liquid mixture, said pump comprising: a housing (3); a rotor (11) mounted in the housing (3); a hollow shaft (19) mounted in the housing and eccentrically relative to the rotor; and at least one displacer (37) which is disposed in the hollow shaft (19) and, at its end (41) remote from the hollow shaft, abuts the rotor. The rotor (11) acts as a drive for the hollow shaft (19).

Description

Pumpe zum Fördern eines MediumsPump for conveying a medium
Beschreibungdescription
Die vorliegende Erfindung betrifft eine Pumpe zum Fördern eines Mediums, insbesondere eines Gas-Flüs¬ sigkeit-Gemisches nach dem Oberbegriff des An¬ spruchs 1.The present invention relates to a pump for conveying a medium, in particular a gas-liquid mixture, according to the preamble of claim 1.
Aus dem Stand der Technik sind Pumpen unterschied¬ lichster Bauart bekannt. So weisen beispielsweise die Radialkolbenpumpen einen Zylinderblock auf, der exzentrisch in einem Gehäuse liegt. In dem Zylin¬ derblock sind Kolben radial angeordnet, die bei der Drehung des Zylinderblocks eine Hubbewegung ausfüh¬ ren, über1icherweise stützen sich die Kolben über Rollen in dem Gehäuse ab. Der Antrieb des Zylinder¬ blocks erfolgt über eine Antriebswelle, die das ge¬ nannte Gehäuse durchdringt und an einem außenlie¬ genden Motor angeschlossen ist.Pumps of various designs are known from the prior art. For example, the radial piston pumps have a cylinder block that is eccentrically located in a housing. Pistons are arranged radially in the cylinder block and perform a lifting movement when the cylinder block rotates. The pistons are supported by rollers in the housing. The cylinder block is driven by a drive shaft which penetrates the housing and is connected to an external motor.
Solche Radialkolbenpumpen haben den Nachteil, daß ihr Aufbau, insbesondere die Kolbenführung im Zy¬ linderblock, relativ aufwendig ausfällt. Darüber hinaus bereiten derartige Pumpen Probleme bei der Förderung von Gas-Flüssigkeits-Gemischen, die ins¬ besondere bei der Erdölförderung anfallen.Radial piston pumps of this type have the disadvantage that their construction, in particular the piston guide in the cylinder block, is relatively complex. In addition, pumps of this type cause problems in the production of gas-liquid mixtures, which occur in particular in the production of crude oil.
Des weiteren muß für die Antriebsseite relativ viel Platz für den eigentlichen Motor und die Antriebs¬ welle vorgesehen sein, wobei die Wellendichtung am Wellendurchbruch im Gehäuse immer wieder zu Schwie¬ rigkeiten fuhren kann.Furthermore, a relatively large amount of space for the actual motor and the drive shaft must be provided for the drive side, the shaft seal on Breakthrough in the housing can lead to difficulties again and again.
Die Aufgabe der vorliegenden Erfindung besteht des¬ halb darin, eine Pumpe vorzusehen, die einen einfa¬ chen und kompakten Aufbau besitzt und zur Forderung von Gas-Flussigkeits-Gemischen einsetzbar ist.The object of the present invention is therefore to provide a pump which has a simple and compact structure and can be used to request gas-liquid mixtures.
Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelost.This object is achieved by the features of claim 1.
Bei der erfindungsgemaßen Losung werden zwei inein¬ ander gesteckte Wellen benutzt, die unabhängig von¬ einander und exzentrisch zueinander in einem Ge¬ häuse gelagert sind. Die innere Welle verfugt über radial verschiebbare Verdranger, die vorzugsweise in einer radialen Bohrung in der Umfangsflache der inneren Welle gefuhrt sind und zusammen mit dem Bohrgrund eine Verdrangerkammer bilden. Durch eine zwischen Bohrlochgrund und der gegenüberliegenden Innenfläche des Verdrangers liegende Feder wird vorteilhafterweise dieser Verdränger an die innere Umfangsflache der äußeren Welle gedruckt. Aufgrund der exzentrischen Anordnung der inneren Welle ver¬ ändert sich der Abstand zwischen dem Bohrlochgrund und der inneren Umfangsflache der äußeren Welle - wahrend einer Umdrehung- kontinuierlich, so daß der Verdränger radial verschoben wird und damit das Raumvolumen der Verdrangerkammer kontinuierlich verändert. Der Antrieb der inneren Welle erfolgt dabei jedoch nicht direkt, sondern indirekt über die äußere Welle, die vorzugsweise die Ankerwicklungen eines Elektromotors aufweist.In the solution according to the invention, two shafts inserted into one another are used, which are mounted independently of one another and eccentrically to one another in a housing. The inner shaft has radially displaceable displacers, which are preferably guided in a radial bore in the circumferential surface of the inner shaft and form a displacement chamber together with the drilling base. By a spring lying between the bottom of the borehole and the opposite inner surface of the displacer, this displacer is advantageously pressed onto the inner peripheral surface of the outer shaft. Because of the eccentric arrangement of the inner shaft, the distance between the bottom of the borehole and the inner circumferential surface of the outer shaft changes continuously during one revolution, so that the displacer is displaced radially and thus the volume of the displacer chamber changes continuously. However, the inner shaft is not driven directly, but indirectly via the outer shaft, which preferably has the armature windings of an electric motor.
Der Vorteil dieser Ausführung besteht darin, daß eine äußerst kompakte Bauweise ermöglicht wird, da die eigentliche Pumpe im Pumpenmotor integriert ist.The advantage of this design is that an extremely compact design is made possible because the actual pump is integrated in the pump motor.
Vorzugsweise dienen die an der inneren Umfangsfla¬ che der äußeren Welle, die gleichzeitig Rotor der Elektromotors ist, als Mitnehmer für die innere Welle, wobei in einer vorteilhaften Weiterbildung die Verdränger mit dem Rotor in Reibschluß stehen. Dadurch läßt sich der Antrieb der exzentrischen in¬ neren Welle mit äußerst geringem Aufwand realisie¬ ren.Preferably, the ones on the inner circumferential surface of the outer shaft, which is also the rotor of the electric motor, serve as drivers for the inner shaft, the displacers being in frictional engagement with the rotor in an advantageous development. This allows the eccentric inner shaft to be driven with extremely little effort.
Vorzugsweise werden der inneren Welle die Medien an einem Wellenende zugeführt und am anderen Wellen¬ ende abgeführt, so daß die innere Welle im wesent¬ lichen linear durchströmt wird. Damit kann die Pumpe ohne weiteres in eine Leitung eingesetzt wer¬ den.The media are preferably fed to the inner shaft at one shaft end and discharged at the other shaft end, so that the flow through the inner shaft is essentially linear. The pump can thus be easily inserted into a line.
In einer weiteren vorteilhaften Ausgestaltung der Erfindung werden mehrere auf der Umfangsflache ver¬ teilte Verdränger vorgesehen, um die Förderleistung in einfacher Weise zu steigern.In a further advantageous embodiment of the invention, a plurality of displacers distributed over the circumferential surface are provided in order to increase the delivery rate in a simple manner.
Weitere vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben. Im folgenden wird nun die vorliegende Erfindung an¬ hand eines Ausfuhrungsbeispiels mit Bezug auf eine Zeichnung naher beschrieben. Dabei zeigt:Further advantageous embodiments of the invention are specified in the subclaims. The present invention will now be described in more detail below with reference to an exemplary embodiment with reference to a drawing. It shows:
Figur 1 eine schematische Darstellung einer er- findungsgemaßen Pumpe im Längsschnitt; undFigure 1 is a schematic representation of a pump according to the invention in longitudinal section; and
Figur 2 schematisch einen einzelnen Verdranger im Längsschnitt.Figure 2 schematically shows a single displacer in longitudinal section.
Die in Figur 1 gezeigte Pumpe 1 besteht aus einem Pumpengehause 3, das beispielsweise zylindrisch ausgebildet sein kann. Die beiden Längsseiten des Pumpengehauses 3 sind mittels anschraubbarer Deckel 5 dichtend abgeschlossen.The pump 1 shown in FIG. 1 consists of a pump housing 3, which can be cylindrical, for example. The two long sides of the pump housing 3 are sealed off by means of a screw-on cover 5.
Im Pumpengehäuse 3 ist ein kompletter Elektromotor untergebracht, wobei in der Figur 1 der Übersicht¬ lichkeit wegen lediglich die Statorwicklung 7 sowie die Anker- beziehungsweise Rotorwicklung 9 schema¬ tisch dargestellt sind. Die übrigen notwendigen Be¬ standteile eines solchen Elektromotors, vorzugswei¬ se eines Gleichstrommotors, sind dem Fachmann be¬ kannt und sollen deshalb an dieser Stelle nicht nä¬ her beschrieben werden.A complete electric motor is accommodated in the pump housing 3, only the stator winding 7 and the armature or rotor winding 9 being shown schematically in FIG. 1 for the sake of clarity. The other necessary components of such an electric motor, preferably a direct current motor, are known to the person skilled in the art and will therefore not be described in more detail here.
Die Ankerwicklung 9 ist in der Umfangsflache einer Welle 11, die im folgenden lediglich als Rotor be¬ zeichnet wird, ausgebildet. Der Rotor 11 ist in ei¬ ner entsprechenden Bohrung in jedem Deckel 5 mit¬ tels eines Lagers, vorzugsweise eines Kugellagers, drehbar gestützt. Somit ist der Rotor 11 um eine Längsachse 17 drehbar.The armature winding 9 is formed in the circumferential surface of a shaft 11, which is referred to below only as a rotor. The rotor 11 is in a corresponding bore in each cover 5 by means of a bearing, preferably a ball bearing, rotatably supported. The rotor 11 is thus rotatable about a longitudinal axis 17.
Innerhalb des Rotors 9 ist eine weitere Welle 19 angeordnet, wobei der Außendurchmesser der Welle 19 geringer als der Innendurchmesser des Rotors 11 ist.A further shaft 19 is arranged within the rotor 9, the outer diameter of the shaft 19 being smaller than the inner diameter of the rotor 11.
Die drehbare Lagerung der Welle 19 erfolgt eben¬ falls über in den beiden Deckeln 5 vorgesehene Boh¬ rungen 21, deren Durchmesser geringer ist als der¬ jenige der Bohrungen 13 und die sich -zur Dek- kelaußenseite hin gesehen- an die Bohrungen 13 an¬ schließen. Die drehbare Abstützung der Welle 19 wird durch Lager 23 gewährleistet.The rotatable mounting of the shaft 19 is also carried out via bores 21 provided in the two covers 5, the diameter of which is smaller than that of the bores 13 and which, viewed towards the outside of the cover, bores against the bores 13 conclude. The rotatable support of the shaft 19 is ensured by bearings 23.
Die beiden Bohrungen 13 und 21 sind jedoch nicht koaxial zueinander, sondern exzentrisch ausgebil¬ det, wobei die Längsachse 17 der Bohrung 13 zu der Längsachse 25 der Bohrungen 21 um einen Betrag v versetzt ist.However, the two bores 13 and 21 are not coaxial to one another, but are formed eccentrically, the longitudinal axis 17 of the bore 13 being offset by an amount v from the longitudinal axis 25 of the bores 21.
Da sowohl der Rotor 11 als auch die Welle 19 rota- tionssyπunetrisch sind, hat diese exzentrische An¬ ordnung zur Folge, daß der Abstand zwischen der äußeren Umfangsflache 27 der Welle 19 und der inne¬ ren Umfangsflache 29 des Rotors 11 -in Umfangsrich- tung gesehen- in einem Bereich von 2v variiert.Since both the rotor 11 and the shaft 19 are rotationally symmetrical, this eccentric arrangement has the consequence that the distance between the outer circumferential surface 27 of the shaft 19 and the inner circumferential surface 29 of the rotor 11 in the circumferential direction seen - varied in a range of 2v.
In der Umfangsflache 27 der Welle 19 sind radial ausgerichtete Ausnehmungen, vorzugsweise Bohrungen 31, eingebracht. Diese Bohrungen 31 sind ihrerseits über Kanäle 33 mit einem die Welle 19 in Längsrich¬ tung durchsetzenden Kanal 35 verbunden.Radially aligned recesses, preferably bores 31, are made in the peripheral surface 27 of the shaft 19. These holes 31 are in turn connected via channels 33 to a channel 35 passing through the shaft 19 in the longitudinal direction.
Eine vergrößerte Darstellung einer solchen Bohrung 31 ist in Figur 2 dargestellt. In der Bohrung ist ein in radialer Richtung verschiebbarer Verdranger 37 gefuhrt. Dieser Verdranger weist eine Becherform auf, wobei das offene Ende 38 dem Bohrlochgrund 39 der Bohrung 31 zugewandt ist.An enlarged illustration of such a bore 31 is shown in FIG. 2. A displacer 37 which can be displaced in the radial direction is guided in the bore. This displacer has a cup shape, the open end 38 facing the bottom 39 of the bore 31.
Um eine gute Fuhrung des Verdrangers 37 in der Boh¬ rung 31 zu erreichen, ist der Außendurchmesser des Verdrangers nur geringfügig kleiner als der Innen¬ durchmesser der Bohrung 31. Das vorzugsweise kalot- tenformige geschlossene Ende des Verdrangers 37 stutzt sich an der inneren Umfangsflache 29 des Ro¬ tors 11 ab. Vorzugsweise ist im Zentrum des kalot- tenformigen Endes ein punktformiger Fortsatz 43 ausgebildet, der somit als Kontaktpunkt zu der Um¬ fangsflache 29 dient.In order to achieve a good guidance of the displacer 37 in the bore 31, the outer diameter of the displacer is only slightly smaller than the inner diameter of the bore 31. The preferably dome-shaped closed end of the displacer 37 is supported on the inner peripheral surface 29 of the rotor 11. A point-shaped extension 43 is preferably formed in the center of the spherical end, which thus serves as a contact point to the peripheral surface 29.
Die Abstutzung des Verdrangers 37 am Bohrlochgrund 39 erfolgt über eine Feder 45, die sich bis zum ge¬ schlossenen Ende des Verdrangers 37 erstreckt.The displacer 37 is supported on the bottom of the borehole 39 by means of a spring 45, which extends to the closed end of the displacer 37.
Die Feder hat dabei die Aufgabe, den Verdranger 37 an die innere Umfangsflache 29 fest anzudrücken.The spring has the task of firmly pressing the displacer 37 against the inner circumferential surface 29.
Der Innenraum des Verdrangers 37 bildet zusammen mit dem darunter liegenden Bohrlochabschnitt eine Verdrangerkammer 47, deren Raumvolumen vom Abstand d zwischen äußerer Umfangsflache 27 und inneren Um¬ fangsflache 29 abhangt. Eine Abdichtung nach außen in den Zwischenraum zwischen Welle 19 und Rotor 11 erfolgt mittels eines O-Rings, der in einer ent¬ sprechenden Nut in der Bohrlochwand der Bohrung 31 sitzt.The interior of the displacer 37 forms, together with the borehole section underneath, a displacement chamber 47, the volume of which depends on the distance d between the outer peripheral surface 27 and the inner peripheral surface 29. A seal to the outside into the space between shaft 19 and rotor 11 by means of an O-ring which sits in a corresponding groove in the borehole wall of bore 31.
Wie bereits erwähnt, ändert sich der Abstand d zwi¬ schen äußerer Umfangsflache 27 und innerer Umfangs¬ flache 29 wahrend einer Umdrehung der Welle 19 kon¬ tinuierlich um einen Betrag 2v. Da der Verdranger 37 durch die Feder 45 ständig an die innere Um¬ fangsflache 29 angedruckt wird, fuhrt die zuvor er¬ wähnte Abstandsanderung zu einer Hubbewegung des Verdrangers 37 in der Bohrung 31 um einen Betrag 2v. Die Hubbewegung wiederum führt zu einer Verän¬ derung des Raumvolumens der Verdrängerkammer 47. Dieser Effekt wird zum Pumpen eines Mediums be¬ nutzt, wobei durch Vergrößern des Raumvolumens über den Kanal 33 Flüssigkeit in die Verdrängerkammer 27 eingesaugt und beim anschließenden Verkleinern des Raumvolumens die Flüssigkeit wieder ausgestoßen wird.As already mentioned, the distance d between the outer circumferential surface 27 and the inner circumferential surface 29 changes continuously by an amount 2v during one revolution of the shaft 19. Since the displacer 37 is constantly pressed against the inner circumferential surface 29 by the spring 45, the previously mentioned change in distance leads to a stroke movement of the displacer 37 in the bore 31 by an amount 2v. The lifting movement in turn leads to a change in the volume of the displacement chamber 47. This effect is used for pumping a medium, liquid being sucked into the displacement chamber 27 via the channel 33 and the liquid again being reduced when the volume of the space is subsequently reduced is expelled.
Die Welle 19 wird vom Rotor 11 angetrieben, in dem die in Reibschluß mit der inneren Umfangsflache 29 stehenden Verdränger 37 die Drehbewegung auf die Welle 19 übertragen. Durch geeignete Wahl des ge¬ schlossenen Endes 41 des Verdrängers 37 und ent¬ sprechende Auslegung der Feder 45 wird verhindert, daß die Umfangsflache 29 über den Verdränger 37 hinweggleitet.The shaft 19 is driven by the rotor 11, in which the displacers 37 which are in frictional engagement with the inner peripheral surface 29 transmit the rotary movement to the shaft 19. A suitable choice of the closed end 41 of the displacer 37 and the corresponding design of the spring 45 prevent the peripheral surface 29 from sliding over the displacer 37.
Da im vorliegenden Fall die Verdranger neben ihrer normalen Funktion auch als Mitnehmer beziehungs- weise Drehmomentübertrager dienen, also keine zu¬ sätzlichen Verbindungsteile zwischen Rotor 11 und Welle 19 notwendig sind, ist ein sehr einfacher und kompakter Aufbau möglich.Since in the present case the displacers not only function normally, but also as carriers or Wise torque transmitters are used, ie no additional connecting parts between the rotor 11 and shaft 19 are necessary, a very simple and compact construction is possible.
Es können jedoch auch andere Mittel zur Übertragung der Drehbewegung vom Rotor 11 auf die Welle 19 vor¬ gesehen werden, beispielsweise Anschläge an der in¬ neren Umfangsflache des Rotors.However, other means for transmitting the rotary movement from the rotor 11 to the shaft 19 can also be provided, for example stops on the inner circumferential surface of the rotor.
Der Pumpbetrieb der Pumpe 1 soll nun mit Bezug auf die Figur 1 erläutert werden.The pumping operation of the pump 1 will now be explained with reference to FIG. 1.
Das zu pumpende Medium, beispielsweise ein Gemisch aus Erdöl und Erdgas, gelangt durch eine Öffnung 51 im Deckel 5 in den Kanal 35 der Welle 19. Durch die Drehung der Welle 19 wird das Medium im Kanal 35 ebenfalls in Drehung versetzt, wobei eine Entmi¬ schung von Flüssigkeit und Gas -bedingt durch die Zentrifugalkraft- erfolgt. Das schwerere Medium, beispielsweise das Erdöl, sammelt sich dabei im Be¬ reich der Wandung des Kanals 35, während das gas¬ förmige Medium sich in einem mittleren Bereich sam¬ melt. Während der Ansaugphase eines Verdrängers 37 wird das Medium durch den Kanal 33 in die Verdrän¬ gerkammer 47 eingesaugt und in der anschließenden Ausstoßphase wieder durch den Kanal 33 in den Kanal 35 gedrückt. Um eine Trennung zwischen Ansaug- und Druckseite herzustellen, sind im Kanal 35, ledig¬ lich schematisch dargestellt, Rückschlagventile 53 vorgesehen. Das ausgestoßene Medium strömt anschließend weiter durch den Kanal 35 in Richtung einer der Öffnung 51 gegenüberliegenden weiteren Öffnung 55 im Deckel 5, wie dies durch Pfeile in der Figur angedeutet ist.The medium to be pumped, for example a mixture of petroleum and natural gas, passes through an opening 51 in the cover 5 into the channel 35 of the shaft 19. The rotation of the shaft 19 also causes the medium in the channel 35 to rotate, with a demixing Liquid and gas are generated by the centrifugal force. The heavier medium, for example petroleum, collects in the area of the wall of the channel 35, while the gaseous medium collects in a central area. During the suction phase of a displacer 37, the medium is sucked through the channel 33 into the displacer chamber 47 and in the subsequent ejection phase is pressed again through the channel 33 into the channel 35. In order to create a separation between the suction and pressure side, check valves 53 are provided in the channel 35, only shown schematically. The ejected medium then flows further through the channel 35 in the direction of a further opening 55 in the cover 5 opposite the opening 51, as is indicated by arrows in the figure.
Im Bereich zwischen den in Figur 1 eingezeichneten Rückschlagventilen 53 ist der Kanal 35 mittels ei¬ ner Trennwand 57 in zwei Kammern 59 aufgeteilt, wo¬ bei die obere Kammer mit der oberen Reihe der Ver¬ drängerkammern und die untere Kammer entsprechend mit der unteren Reihe der Verdrängerkammern verbun¬ den sind. So kann beispielsweise das vom oberen Verdränger ausgestoßene Medium nicht in die Ver¬ drängerkammer des unteren ansaugenden Verdrängers gelangen.In the area between the check valves 53 shown in FIG. 1, the channel 35 is divided into two chambers 59 by means of a partition 57, the upper chamber with the upper row of displacement chambers and the lower chamber correspondingly with the lower row of Displacement chambers are connected. For example, the medium expelled from the upper displacer cannot get into the displacement chamber of the lower aspirating displacer.
Selbstverständlich sind auch andere Lösungen mög¬ lich, solange eine Trennung zwischen ansaugenden und ausstoßenden Verdrängern vorhanden ist.Of course, other solutions are also possible as long as there is a separation between the suction and ejection displacers.
Beispielsweise wäre denkbar, statt eines gemeinsa¬ men Kanals 33 zu einem Verdränger, zwei getrennte Kanäle auszubilden, wobei der Ansaugkanal mit der Öffnung 51 und der Ausstoßkanal mit der Öffnung 55 in Verbindung steht. Auch hier müssen jedoch Rück¬ schlagventile im Ansaug- und Ausstoßkanalsystem vorhanden sein.For example, it would be conceivable to form two separate channels instead of a common channel 33 to form a displacer, the suction channel being connected to the opening 51 and the exhaust channel being connected to the opening 55. Here too, however, check valves must be present in the intake and exhaust duct system.
Die Pumpleistung der in Figur 1 gezeigten Pumpe kann durch Erhöhung der Verdrängeranzahl weiter ge¬ steigert werden. Die vorliegende Pumpe kann für die unterschiedlich¬ sten Anwendungsgebiete und Druckbereiche eingesetzt werden.The pump capacity of the pump shown in FIG. 1 can be increased further by increasing the number of displacers. The present pump can be used for the most varied fields of application and pressure ranges.
Daruberhinaus laßt sich durch Umkehr der Me¬ dienstrome die zuvor beschriebene Pumpe auch als Motor verwenden. In addition, by reversing the media streams, the pump described above can also be used as a motor.

Claims

Ansprüche Expectations
1. Pumpe zum Fordern eines Mediums, insbesondere eines Gas-Flussigkeits-Gemisches mit einem Gehäuse (3) ; einem im Gehäuse (3) gelagerten Rotor (11) ; einer im Gehäuse und exzentrisch zum Rotor gelager¬ ten Hohlwelle (19) ; und wenigstens einem Verdranger (37), der in der Hohlwelle (19) angeordnet ist und mit seinem der Hohlwelle abgewandten Ende (41) am Rotor anliegt, dadurch gekennzeichnet, daß der Ro¬ tor (11) als Antrieb für die Hohlwelle (19) dient.1. Pump for conveying a medium, in particular a gas-liquid mixture with a housing (3); a rotor (11) mounted in the housing (3); a hollow shaft (19) mounted in the housing and eccentrically to the rotor; and at least one displacer (37) which is arranged in the hollow shaft (19) and abuts the rotor with its end (41) facing away from the hollow shaft, characterized in that the rotor (11) acts as a drive for the hollow shaft (19) serves.
2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß ein Mitnehmer zwischen Rotor (11) und Hohlwelle (19) angeordnet ist.2. Pump according to claim 1, characterized in that a driver between the rotor (11) and hollow shaft (19) is arranged.
3. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Verdranger (37) als Mitnehmer dient.3. Pump according to one of the preceding claims, characterized in that the displacer (37) serves as a driver.
4. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Verdränger (37) mit dem Rotor (11) in Reibschluß steht.4. Pump according to one of the preceding claims, characterized in that the displacer (37) with the rotor (11) is in frictional engagement.
5. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Hohlwelle (19) als Medienzuführung und Medienabfuhrung dient. 5. Pump according to one of the preceding claims, characterized in that the hollow shaft (19) serves as a media feed and media discharge.
6. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Verdranger (37) in einer entsprechenden radialen Ausnehmung (31) in der Hohlwelle (19) verschiebbar gefuhrt ist.6. Pump according to one of the preceding claims, characterized in that the displacer (37) is guided in a corresponding radial recess (31) in the hollow shaft (19).
7. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß sich der Verdränger (37) am Grund (39) der Ausnehmung (31) über eine Feder abstutzt.7. Pump according to one of the preceding claims, characterized in that the displacer (37) on the base (39) of the recess (31) is supported by a spring.
8. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß ein Dichtungselement (49) der Umfangsflache des Verdrängers (37) zuge¬ ordnet ist.8. Pump according to one of the preceding claims, characterized in that a sealing element (49) of the peripheral surface of the displacer (37) is assigned.
9. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Ausnehmung mit der Medienzuführung und der Medienabführung verbunden ist, wobei der Medienabfuhrung und/oder der Medien¬ zuführung ein Rückschlagventil zugeordnet ist.9. Pump according to one of the preceding claims, characterized in that the recess is connected to the media feed and the media discharge, with a check valve being assigned to the media discharge and / or the media feed.
10. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß mehrere Verdränger (37) in der Hohlwelle (19) vorgesehen sind.10. Pump according to one of the preceding claims, characterized in that a plurality of displacers (37) are provided in the hollow shaft (19).
11. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die mehreren Verdränger in Längs- und/oder in Umfangsrichtung der Hohlwelle (19) gleichmäßig verteilt sind.11. Pump according to one of the preceding claims, characterized in that the plurality of displacers in the longitudinal and / or in the circumferential direction of the hollow shaft (19) are evenly distributed.
12. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Rotor (11) Teil ei¬ nes Elektromotors (7, 9) ist, wobei die Medienzu¬ fuhrung und -abfuhrung axial zum Motor erfolgt. 12. Pump according to one of the preceding claims, characterized in that the rotor (11) is part of an electric motor (7, 9), the media supply and removal taking place axially to the motor.
13. Verwendung einer Pumpe nach einem der Ansprüche 1 - 12 als Motor. 13. Use of a pump according to one of claims 1-12 as a motor.
PCT/EP1996/000015 1995-01-05 1996-01-04 Pump for conveying a medium WO1996021108A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP96900298A EP0813654A1 (en) 1995-01-05 1996-01-04 Pump for conveying a medium
JP8520731A JPH11502277A (en) 1995-01-05 1996-01-04 Pump to send media
AU43904/96A AU4390496A (en) 1995-01-05 1996-01-04 Pump for conveying a medium

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19500246 1995-01-05
DE19504366.9 1995-02-10
DE19504366A DE19504366C1 (en) 1995-01-05 1995-02-10 Pump for conveying a medium
DE19500246.6 1995-02-10

Publications (1)

Publication Number Publication Date
WO1996021108A1 true WO1996021108A1 (en) 1996-07-11

Family

ID=26011469

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1996/000015 WO1996021108A1 (en) 1995-01-05 1996-01-04 Pump for conveying a medium

Country Status (4)

Country Link
EP (1) EP0813654A1 (en)
JP (1) JPH11502277A (en)
AU (1) AU4390496A (en)
WO (1) WO1996021108A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2526844A (en) * 2014-06-05 2015-12-09 Stratec Biomedical Ag Liquid waste handling

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5265609B2 (en) * 2010-03-29 2013-08-14 住友重機械工業株式会社 Fluid pressure generator

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB506195A (en) * 1938-01-19 1939-05-24 Charles Hyland Improvements in revolving cylinder-reciprocating piston pumps
CH393924A (en) * 1961-08-16 1965-06-15 Schweizerische Lokomotiv Radial piston pump with variable delivery rate
CH406853A (en) * 1961-04-28 1966-01-31 Schweizerische Lokomotiv Piston pump
DE2359734B1 (en) * 1973-11-27 1974-12-05 Gebrueder Sulzer Ag, Winterthur (Schweiz) Hydrostatic piston engine
EP0450586A1 (en) * 1990-04-04 1991-10-09 Yasuo Kita Rotary type fluid energy converter

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB506195A (en) * 1938-01-19 1939-05-24 Charles Hyland Improvements in revolving cylinder-reciprocating piston pumps
CH406853A (en) * 1961-04-28 1966-01-31 Schweizerische Lokomotiv Piston pump
CH393924A (en) * 1961-08-16 1965-06-15 Schweizerische Lokomotiv Radial piston pump with variable delivery rate
DE2359734B1 (en) * 1973-11-27 1974-12-05 Gebrueder Sulzer Ag, Winterthur (Schweiz) Hydrostatic piston engine
EP0450586A1 (en) * 1990-04-04 1991-10-09 Yasuo Kita Rotary type fluid energy converter

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2526844A (en) * 2014-06-05 2015-12-09 Stratec Biomedical Ag Liquid waste handling

Also Published As

Publication number Publication date
AU4390496A (en) 1996-07-24
JPH11502277A (en) 1999-02-23
EP0813654A1 (en) 1997-12-29

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