EP0323834A2 - Sealless pump - Google Patents

Sealless pump Download PDF

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Publication number
EP0323834A2
EP0323834A2 EP89100066A EP89100066A EP0323834A2 EP 0323834 A2 EP0323834 A2 EP 0323834A2 EP 89100066 A EP89100066 A EP 89100066A EP 89100066 A EP89100066 A EP 89100066A EP 0323834 A2 EP0323834 A2 EP 0323834A2
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EP
European Patent Office
Prior art keywords
seal
pump according
housing
drive spindle
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP89100066A
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German (de)
French (fr)
Other versions
EP0323834A3 (en
Inventor
Werner Dr. Moser
Klaus Albrecht
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Leistritz AG
Original Assignee
Leistritz AG
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
Application filed by Leistritz AG filed Critical Leistritz AG
Publication of EP0323834A2 publication Critical patent/EP0323834A2/en
Publication of EP0323834A3 publication Critical patent/EP0323834A3/en
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/008—Enclosed motor pump units
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F04C2/165—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type having more than two rotary pistons with parallel axes

Definitions

  • the invention relates to a seal-free pump in which a drive spindle, which is in drive connection with an electric motor, and at least one, preferably two, meshing running spindle (s) are mounted in a housing.
  • Seal-free pumps of the type described above are usually constructed in such a way that the actual screw pump with its housing is flanged directly to the electric motor, the drive spindle being rigidly connected to the rotor of the electric motor.
  • the disadvantage here is the fact that the longitudinal dimension of such a pump corresponds in any case to the sum of the lengths of the screw pump and the electric motor.
  • a pump has been developed in accordance with P 37 01 586, in which the screw pump and the electric motor are integrated in one component.
  • the drive spindle which is held in the motor housing in a rotationally fixed manner
  • the two running spindles which transport the pumped medium from the suction side to the pressure side are installed directly in a corresponding, internally profiled hollow rotor of the electric motor, so that a separate pump housing is no longer required.
  • this embodiment which has already proven itself extremely well in operation, has the disadvantage that, despite its dimensions being many times smaller than those of conventional pumps, its overall height is nevertheless relatively large.
  • the invention is therefore based on the object of designing a seal-free pump in such a way that using the force of the conveying medium, using few and geometrically simple components, which can also be manufactured from chemically resistant plastics, and the construction height is further reduced in quiet and low-pulsation operation, which means that it can also be used in confined spaces, as can often be found in the chemical industry.
  • the invention provides that the rotor of the electric motor surrounds the outer cylindrical pump housing and is mounted at one end by connection to the drive spindle.
  • the configuration of the seal-free pump according to the invention results in a very simple, and at the same time space-saving design, since additional measures both for mounting the rotor and for connecting the rotor and the driving drive spindle can be omitted.
  • the rotor is supported on the end by a one-sided rigid connection to the drive spindle. Accordingly, on the one hand, with the rotor being fixed on the drive spindle, its mounting is realized in the simplest way, without additional support or bearing points having to be provided for this within the construction. On the other hand, it is also ensured that the drive spindle can actually act as the drive element of the pump via the rotor.
  • the pump housing is axially immovably mounted in the suction-side flange cover and is supported on the pressure side via the meshing running spindles and offset by 90 ° directly on the drive spindle. This measure also ensures that the exposed end of the fixed pump housing and the two running spindles attached therein are fixed in the radial direction simply by the mounting of the intermediate spindle.
  • the invention provides that the drive spindle has an axial through bore, whereby aromatic lubrication of the axial fixation of the drive spindle by the pumped medium is achieved. It is also within the scope of the invention to arrange a safety valve which is axially coaxial with the drive spindle and which, at the time of overload, i. This means that if a differential pressure value between the suction and pressure side specified by the user is exceeded, it responds and enables short overflow paths due to its position and consists of a few additional components.
  • the invention provides that bores are arranged in the suction-side region of the housing in such a way that the pressure-side conveying medium acts on flat surfaces of the meshing running spindles.
  • This measure independently of the drive spindle axially supports the pair of running spindles by axially balancing the force of each running spindle using the fluid that flows through a hole in the housing from the pressure side and builds up the necessary counterforce on the respective flat surface, whereby this is determined via the previously determined one Area size is adapted to the given conditions.
  • the rotor in the outlet region of the pump is also provided with a number of through-openings which increase the pulsation frequency of the pump depending on the division, so that the pulsation damping can be carried out more easily by a subsequent pulsation damping device in the form of a sieve of appropriate mesh size.
  • the throughflow openings can additionally be profiled such that the conveying medium is accelerated in the sense of an impeller of a turbomachine and then flows through a stator blade blading as a pulsation damping device instead of through a screen.
  • a stator 4 is fixed and a rotor 5 rotatably in the form of a bell.
  • the rotor 5, the surrounds the outer cylindrical pump housing 6, is in the exemplary embodiment according to FIG. 1 connected via its one end 7 to the drive spindle 8 in a floating manner.
  • one end 9 of the pump housing 6 is received by the suction-side flange cover 2 and held axially immovably therein, for example by a pin 10, while the other end 11 of the pump housing 6 rotates on the pressure side via the meshing running spindles 12 and offset by 90 ° is supported on the drive spindle 8.
  • the drive spindle 8 is supported with one end 13 in the pressure-side flange cover 3 and with the other end 15 facing the suction chamber 14 in a housing insert 16. Furthermore, the drive spindle 8 has an axial through-bore 17 through which the pumped medium flows from the pressure side in the direction of the suction side and strikes the safety valve 22. As a result, an axial force compensation is generated, by means of which the drive spindle 8 remains in its predetermined position, which can be adjusted as desired, in particular by changing the safety valve 22, depending on the respective operating conditions and needs of the user.
  • each of the running spindles 12 is provided in the suction-side region of the housing 6 with a flat surface 19 on a pin 20, which is acted upon via a bore 21 in the housing 6 and in the housing insert 16 with pressure-side delivery medium for axial force compensation.
  • a safety valve 22 is arranged coaxially with the drive spindle 8 and directly in the suction chamber 14, which is exerted by excessive forces when the The fluid on the pressure side opens automatically, thus relieving the pressure, ie relieving the excess pressure.
  • the rotor 5 is provided in the outlet region 23 of the pump with a series of flow openings 24 which increase the pulsation frequency of the pump depending on the division.
  • the pulsation damping can take place more easily.
  • the throughflow openings 24 can be profiled such that the conveying medium is accelerated in the sense of an impeller of a turbomachine and then flows through a stator blade blading (not shown in the figures) as the provided pulsation damping device 25 instead of through a sieve.
  • the rotor 5 is not supported overhung, but is supported on the end 28 opposite the end 7 by a support ring 27 on the pump housing 6.
  • the invention is not limited to the exemplary embodiments shown. In particular, it would also be possible to provide only a single component instead of a housing 6 and housing insert 16 that are separate from one another, or to design the threaded connections 26 on both sides as flange connections.
  • the pump according to the invention is also suitable for both a submerged and a non-submerged mode of operation in accordance with the requirements of the user.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Sealless pump on which a drive spindle in a housing is drive-connected to an electric motor and at least one, preferably two, meshing working spindle(s) are supported, preferably for conveying low-viscosity fluids, the rotor of the electric motor enclosing the external cylindrical pump housing and being supported at one end by connection with the drive spindle. <IMAGE>

Description

Die Erfindung bezieht sich auf eine dichtungsfreie Pumpe, bei der in einem Gehäuse eine Antriebsspindel, die in An­triebsverbindung mit einem Elektromotor steht, und wenig­stens eine, vorzugsweise zwei, mit ihr kämmende Laufspin­del(n) gelagert sind.The invention relates to a seal-free pump in which a drive spindle, which is in drive connection with an electric motor, and at least one, preferably two, meshing running spindle (s) are mounted in a housing.

Dichtungsfreie Pumpen der vorstehend beschriebenen Art sind üblicherweise derart aufgebaut, daß die eigentliche Schrau­benpumpe mit ihrem Gehäuse unmittelbar an den Elektromotor angeflanscht ist, wobei die Antriebsspindel mit dem Rotor des Elektromotors starr verbunden ist. Nachteilig hierbei ist jedoch die Tatsache, daß die Längsabmessung einer sol­chen Pumpe in jedem Fall der Summe der Längen von Schrau­benpumpe und Elektromotor entspricht. Um u.a. die Bauhöhe von diesen Pumpen zu verkleinern, ist eine Pumpe gemäß P 37 01 586 entwickelt worden, bei welcher die Schrauben­pumpe und der Elektromotor in einem Bauteil integriert sind. So werden einerseits die drehfest im Motorgehäuse ge­haltene Antriebsspindel und andererseits die beiden das Fördermedium von der Saugseite zur Druckseite weitertransportierenden Laufspindeln direkt in einen entsprechenden, innenprofilierten hohlen Rotor des Elektro­motors eingebaut, so daß ein gesondertes Pumpengehäuse nicht mehr benötigt wird. Diese im Betrieb schon außeror­dentlich bewährte Ausführungsform hat jedoch den Nachteil, daß trotz ihrer gegenüber üblichen Pumpen um ein vielfaches verkleinerten Abmessungen deren Bauhöhe dennoch verhältnis­mäßig groß ist.Seal-free pumps of the type described above are usually constructed in such a way that the actual screw pump with its housing is flanged directly to the electric motor, the drive spindle being rigidly connected to the rotor of the electric motor. The disadvantage here, however, is the fact that the longitudinal dimension of such a pump corresponds in any case to the sum of the lengths of the screw pump and the electric motor. To i.a. To reduce the height of these pumps, a pump has been developed in accordance with P 37 01 586, in which the screw pump and the electric motor are integrated in one component. On the one hand, the drive spindle, which is held in the motor housing in a rotationally fixed manner, and on the other hand, the two running spindles which transport the pumped medium from the suction side to the pressure side are installed directly in a corresponding, internally profiled hollow rotor of the electric motor, so that a separate pump housing is no longer required. However, this embodiment, which has already proven itself extremely well in operation, has the disadvantage that, despite its dimensions being many times smaller than those of conventional pumps, its overall height is nevertheless relatively large.

Der Erfindung liegt daher die Aufgabe zugrunde, eine dich­tungsfreie Pumpe so auszugestalten, daß unter Ausnutzung der Kraftwirkung des Fördermediums, unter Verwendung von wenigen und geometrisch einfachen Bauteilen, die damit auch aus chemisch resistenten Kunststoffen herstellbar sind, so­wie bei leisem und pulsationsarmen Betrieb die Bauhöhe wei­ter verkleinert wird, wodurch diese auch unter beengten Raumverhältnissen, wie sie in der chemischen Industrie oft vorzufinden sind, einsetzbar ist.The invention is therefore based on the object of designing a seal-free pump in such a way that using the force of the conveying medium, using few and geometrically simple components, which can also be manufactured from chemically resistant plastics, and the construction height is further reduced in quiet and low-pulsation operation, which means that it can also be used in confined spaces, as can often be found in the chemical industry.

Zur Lösung dieser Aufgabe ist erfindungsgemäß vorgesehen, daß der Rotor des Elektromotors das außenzylindrische Pum­pengehäuse umgibt und an einem Ende durch Verbindung mit der Antriebsspindel gelagert ist.To achieve this object, the invention provides that the rotor of the electric motor surrounds the outer cylindrical pump housing and is mounted at one end by connection to the drive spindle.

Durch die erfindungsgemäße Ausgestaltung der dichtungs­freien Pumpe ergibt sich eine sehr einfache, zugleich auch platzsparende Bauweise, da zusätzliche Maßnahmen sowohl zur Lagerung des Rotors als auch zur Verbindung von Rotor und antreibender Antriebsspindel entfallen können. In einer er­sten bevorzugten Ausführungsform kann dabei vorgesehen sein, daß der Rotor durch einseitige starre Verbindung mit der Antriebsspindel am Ende fliegend gelagert ist. Demnach ist einerseits mit der Festlegung des Rotors auf der An­triebsspindel dessen Lagerung auf einfachste Weise reali­siert, ohne daß weitere Stütz- bzw. Lagerpunkte innerhalb der Konstruktion hierfür vorzusehen sind. Andererseits ist zugleich sichergestellt, daß die Antriebsspindel über den Rotor auch tatsächlich als Antriebsglied der Pumpe wirken kann.The configuration of the seal-free pump according to the invention results in a very simple, and at the same time space-saving design, since additional measures both for mounting the rotor and for connecting the rotor and the driving drive spindle can be omitted. In a first preferred embodiment it can be provided that the rotor is supported on the end by a one-sided rigid connection to the drive spindle. Accordingly, on the one hand, with the rotor being fixed on the drive spindle, its mounting is realized in the simplest way, without additional support or bearing points having to be provided for this within the construction. On the other hand, it is also ensured that the drive spindle can actually act as the drive element of the pump via the rotor.

Andererseits ist aber auch ohne nennenswerten zusätzlichen Aufwand eine Ausführungsform möglich, bei der die Ausbil­dung so getroffen ist, daß der Rotor an dem dem Ende gegen­überliegenden Ende über einen Abstützring auf dem Pumpenge­häuse gelagert ist.On the other hand, however, an embodiment is also possible without significant additional effort, in which the design is such that the rotor is mounted on the pump housing at the end opposite the end via a support ring.

In diesem Zusammenhang ist es im Rahmen der Erfindung wei­terhin vorgesehen, daß das Pumpengehäuse axial unverschieb­bar in dem saugseitigen Flanschdeckel gelagert ist und sich druckseitig über die kämmenden Laufspindeln und um 90° ver­setzt direkt auf der Antriebsspindel abstützt. Durch diese Maßnahme wird ebenfalls gewährleistet, daß schon alleine durch die Lagerung der Zwischenspindel das freiliegende Ende des feststehenden Pumpengehäuses sowie die beiden darin angebrachten Laufspindeln in radialer Richtung fest­gelegt sind.In this context, it is further provided in the context of the invention that the pump housing is axially immovably mounted in the suction-side flange cover and is supported on the pressure side via the meshing running spindles and offset by 90 ° directly on the drive spindle. This measure also ensures that the exposed end of the fixed pump housing and the two running spindles attached therein are fixed in the radial direction simply by the mounting of the intermediate spindle.

In weiterer Ausgestaltung sieht die Erfindung vor, daß die Antriebsspindel eine axiale Durchgangsbohrung aufweist, wo­durch aromatisch eine Schmierung der axialen Festlegung der Antriebsspindel von dem Fördermedium erzielt wird. Wei­ter liegt es im Rahmen der Erfindung, ein zur Antriebsspin­del achsgleiches Sicherheitsventil unmittelbar in Saugraum anzuordnen, welches im Zeitpunkt der Überlastung, d.h. also bei überschreiten eines vom Anwender vorgegebenen Diffe­renzdruckwertes zwischen Saug- und Druckseite, anspricht und durch seine Lage kurze Überströmwege ermöglicht sowie aus wenigen zusätzlichen Bauteilen besteht.In a further embodiment, the invention provides that the drive spindle has an axial through bore, whereby aromatic lubrication of the axial fixation of the drive spindle by the pumped medium is achieved. It is also within the scope of the invention to arrange a safety valve which is axially coaxial with the drive spindle and which, at the time of overload, i. This means that if a differential pressure value between the suction and pressure side specified by the user is exceeded, it responds and enables short overflow paths due to its position and consists of a few additional components.

Darüber hinaus sieht die Erfindung vor, daß im saugseitigen Bereich des Gehäuses Bohrungen derart angeordnet sind, daß druckseitiges Fördermedium auf Planflächen der kämmenden Laufspindeln wirkt. Durch diese Maßnahme wird unabhängig von der Antriebsspindel das Laufspindelpaar axial gehal­tert, indem der axiale Kräfteausgleich einer jeden Lauf­spindel mittels Fördermedium erfolgt, welches durch eine Bohrung im Gehäuse von der Druckseite herströmt und an der jeweiligen Planfläche die notwendige Gegenkraft aufbaut, wobei diese über die vorher bestimmte Flächengröße den vor­gegebenen Bedingungen angepaßt wird.In addition, the invention provides that bores are arranged in the suction-side region of the housing in such a way that the pressure-side conveying medium acts on flat surfaces of the meshing running spindles. This measure independently of the drive spindle axially supports the pair of running spindles by axially balancing the force of each running spindle using the fluid that flows through a hole in the housing from the pressure side and builds up the necessary counterforce on the respective flat surface, whereby this is determined via the previously determined one Area size is adapted to the given conditions.

Schließlich ist erfindungsgemäß noch der Rotor im Aus­trittsbereich der Pumpe mit einer Anzahl von Durchströmöff­nungen versehen, die die Pulsationsfrequenz der Pumpe je nach Teilung erhöht, so daß durch eine anschließende Pulsa­tionsdämpfungseinrichtung in Form eines Siebes entsprechen­der Maschenweite die Pulsationsdämpfung leichter erfolgen kann. Erfindungsgemäß können zusätzlich die Durchströmöff­nungen so profiliert sein, daß im Sinne eines Laufrades ei­ner Strömungsmaschinew das Fördermedium beschleunigt wird und anschließend anstelle durch ein Sieb durch eine Leitradbeschaufelung als Pulsationsdämpfungseinrichtung fließt.Finally, according to the invention, the rotor in the outlet region of the pump is also provided with a number of through-openings which increase the pulsation frequency of the pump depending on the division, so that the pulsation damping can be carried out more easily by a subsequent pulsation damping device in the form of a sieve of appropriate mesh size. According to the invention, the throughflow openings can additionally be profiled such that the conveying medium is accelerated in the sense of an impeller of a turbomachine and then flows through a stator blade blading as a pulsation damping device instead of through a screen.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines Aus­führungsbeispieles sowie anhand der Zeichnung, wobei darauf verwiesen wird, daß beidseitige Gewindeanschlüsse auch Flanschanschlüsse sein können und die Pumpe ohne jegliche Änderung als getauchte und/oder nichtgetauchte Version zum Einsatz kommen kann. Dabei zeigen:

  • Fig. 1 einen Längsschnitt durch eine erfindungsgemäße dichtungsfreie Pumpe,
  • Fig. 2 einen Querschnitt durch das feststehende Pumpenge­häuse, und
  • Fig. 3 einen Längsschnitt durch eine abgewandelte Pumpe.
Further advantages, features and details of the invention emerge from the following description of an exemplary embodiment and from the drawing, reference being made to the fact that threaded connections on both sides can also be flange connections and the pump can be used as a submerged and / or non-submerged version without any change . Show:
  • 1 shows a longitudinal section through a seal-free pump according to the invention,
  • Fig. 2 shows a cross section through the fixed pump housing, and
  • Fig. 3 shows a longitudinal section through a modified pump.

In dem Gehäuse 1 eines Elektromotors, versehen mit einem saugseitigen Flanschdeckel 2 und einem druckseitigen Flan­schdeckel 3, ist feststehend ein Stator 4 und drehbar ein Rotor 5 in Form einer Glocke angeordnet. Der Rotor 5, der das außenzylindrische Pumpengehäuse 6 umgibt, ist dabei im Ausführungsbeispiel nach Fig. 1 über sein eines Ende 7 mit der Antriebsspindel 8 fliegend gelagert verbunden. Des wei­teren wird ein Ende 9 des Pumpengehäuses 6 von dem saugsei­tigen Flanschdeckel 2 aufgenommen und in diesem axial un­verschiebbar, beispielsweise durch einen Stift 10, gehal­tert, während sich das andere Ende 11 des Pumpengehäuses 6 druckseitig über die kämmenden Laufspindeln 12 und um 90° versetzt drekt auf der Antriebsspindel 8 abstützt. Hier­durch wird eine außerordentlich kompakte Bauweise erreicht, die sich folglich dafür verantwortlich zeigt, daß die dich­tungsfreie Pumpe sehr klein baut und daher unter auch außerordentlich beengten Raumverhältnissen einsetzbar ist. Die Antriebsspindel 8 ist mit einem Ende 13 in dem druckseitigen Flanschdeckel 3 und mit dem anderen dem Saug­raum 14 zugekehrten Ende 15 in einem Gehäuseeinsatz 16 ge­lagert. Weiterhin weist die Antriebsspindel 8 eine axiale Durchgangsbohrung 17 auf, durch die das Fördermedium von der Druckseite in Richtung Saugseite strömt und auf das Sicherheitsventil 22 auftrifft. Hierdurch wird ein axialer Kraftausgleich erzeugt, mittels welchem die Antriebsspindel 8 in ihrer vorbestimmten Lage verbleibt, die insbesondere durch Veränderung des Sicherheitsventils 22 abhängig von den jeweiligen Einsatzbedingungen und -bedürfnissen des An­wenders beliebig einstellbar ist. Zur Sicherstellung eines axialen Schubausgleichs der Laufspindeln 12 ist jeder der Laufspindeln 12 im saugseitigen Bereich des Gehäuses 6 mit einer Planfläche 19 an einem Zapfen 20 versehen, die über eine Bohrung 21 im Gehäuse 6 und im Gehäuseeinsatz 16 mit druckseitigem Fördermedium zum axialen Kraftausgleich beaufschlagt ist. In dem Gehäuseeinsatz 16 ist, wie oben erwähnt, ein Sicherheitsventil 22 achsgleich zur Antriebsspindel 8 und unmittelbar im Saugraum 14 angeord­net, das sich bei Auftreten zu großer Kräfte durch das druckseitige Fördermedium automatisch öffnet und somit für eine Entlastung, d.h. Abbau des Überdrucks, sorgt. Schließ­lich ist der Rotor 5 im Austrittsbereich 23 der Pumpe mit einer Reihe von Durchströmöffnungen 24 versehen, die die Pulsationsfrequenz der Pumpe je nach Teilung erhöht. Mit­tels einer anschließenden Pulsationsdämpfungseinrichtung 25 in Form eines Siebes 25 entsprechender Maschenweite kann die Pulsationsdämpfung leichter erfolgen. Zusätzlich können die Durchströmöffnungen 24 derart profiliert sein, daß im Sinne eines Laufrades einer Strömungsmaschine das Förderme­dium beschleunigt wird und anschließend anstelle durch ein Sieb durch eine in den Figuren nicht dargestellte Leitradbeschaufelung als vorgesehene Pulsationsdämpfungs­einrichtung 25 fließt.In the housing 1 of an electric motor, provided with a suction-side flange cover 2 and a pressure-side flange cover 3, a stator 4 is fixed and a rotor 5 rotatably in the form of a bell. The rotor 5, the surrounds the outer cylindrical pump housing 6, is in the exemplary embodiment according to FIG. 1 connected via its one end 7 to the drive spindle 8 in a floating manner. Furthermore, one end 9 of the pump housing 6 is received by the suction-side flange cover 2 and held axially immovably therein, for example by a pin 10, while the other end 11 of the pump housing 6 rotates on the pressure side via the meshing running spindles 12 and offset by 90 ° is supported on the drive spindle 8. As a result, an extremely compact design is achieved, which is therefore responsible for the fact that the seal-free pump is very small and can therefore be used even in extremely cramped spaces. The drive spindle 8 is supported with one end 13 in the pressure-side flange cover 3 and with the other end 15 facing the suction chamber 14 in a housing insert 16. Furthermore, the drive spindle 8 has an axial through-bore 17 through which the pumped medium flows from the pressure side in the direction of the suction side and strikes the safety valve 22. As a result, an axial force compensation is generated, by means of which the drive spindle 8 remains in its predetermined position, which can be adjusted as desired, in particular by changing the safety valve 22, depending on the respective operating conditions and needs of the user. To ensure axial thrust compensation of the running spindles 12, each of the running spindles 12 is provided in the suction-side region of the housing 6 with a flat surface 19 on a pin 20, which is acted upon via a bore 21 in the housing 6 and in the housing insert 16 with pressure-side delivery medium for axial force compensation. In the housing insert 16, as mentioned above, a safety valve 22 is arranged coaxially with the drive spindle 8 and directly in the suction chamber 14, which is exerted by excessive forces when the The fluid on the pressure side opens automatically, thus relieving the pressure, ie relieving the excess pressure. Finally, the rotor 5 is provided in the outlet region 23 of the pump with a series of flow openings 24 which increase the pulsation frequency of the pump depending on the division. By means of a subsequent pulsation damping device 25 in the form of a sieve 25 with a corresponding mesh size, the pulsation damping can take place more easily. In addition, the throughflow openings 24 can be profiled such that the conveying medium is accelerated in the sense of an impeller of a turbomachine and then flows through a stator blade blading (not shown in the figures) as the provided pulsation damping device 25 instead of through a sieve.

Beim Ausführungsbeispiel nach Fig. 3 ist der Rotor 5 nicht fliegend gelagert, sondern an dem dem Ende 7 gegenüberlie­genden Ende 28 durch einen Abstützring 27 auf dem Pumpen­gehäuse 6 gelagert.In the exemplary embodiment according to FIG. 3, the rotor 5 is not supported overhung, but is supported on the end 28 opposite the end 7 by a support ring 27 on the pump housing 6.

Die Erfindung ist nicht nur auf die dargestellten Ausfüh­rungsbeispiele beschränkt. So wäre es insbesondere auch möglich, statt eines voneinander getrennten Gehäuses 6 und Gehäuseeinsatzes 16 nur ein einziges Bauteil vorzusehen oder die beidseitigen Gewindeanschlüsse 26 auch als Flan­schanschlüsse auszubilden. Auch ist die erfindungsgemäße Pumpe sowohl für eine getauchte als auch eine nichtge­tauchte Betriebsweise entsprechend den Anforderungen von seiten des Anwenders geeignet.The invention is not limited to the exemplary embodiments shown. In particular, it would also be possible to provide only a single component instead of a housing 6 and housing insert 16 that are separate from one another, or to design the threaded connections 26 on both sides as flange connections. The pump according to the invention is also suitable for both a submerged and a non-submerged mode of operation in accordance with the requirements of the user.

Claims (9)

1. Dichtungsfreie Pumpe, bei der in einem Gehäuse eine Antriebsspindel, die in Antriebsverbindung mit einem Elektromotor steht, und wenigstens eine, vorzugsweise zwei, mit ihr kämmende Laufspindel(n) gelagert sind, vorzugsweise zum Fördern von niedrig viskosen Flüs­sigkeiten, dadurch gekennzeichnet, daß der Rotor (5) des Elektromotors das außenzylindrische Pumpengehäuse (6) umgibt und an einem Ende (7) durch Verbindung mit der Antriebsspindel (8) gelagert ist.1. Seal-free pump, in which in a housing a drive spindle, which is in drive connection with an electric motor, and at least one, preferably two, meshing with it running spindle (s), preferably for conveying low-viscosity liquids, characterized in that the rotor (5) of the electric motor surrounds the outer cylindrical pump housing (6) and is supported at one end (7) by connection to the drive spindle (8). 2. Dichtungsfreie Pumpe nach Anspruch 1, dadurch gekenn­zeichnet, daß der Rotor (5) durch einseitige starre Verbindung mit der Antriebsspindel (8) am Ende (7) fliegend gelagert ist.2. Seal-free pump according to claim 1, characterized in that the rotor (5) is overhung by one-sided rigid connection to the drive spindle (8) at the end (7). 3. Dichtungsfreie Pumpe nach Anspruch 1, dadurch gekenn­zeichnet, daß der Rotor (5) an dem dem Ende (7) ge­genüberliegenden Ende (28) über einen Abstützring (27) auf dem Pumpengehäuse (6) gelagert ist.3. Seal-free pump according to claim 1, characterized in that the rotor (5) at the end (7) opposite end (28) via a support ring (27) is mounted on the pump housing (6). 4. Dichtungsfreie Pumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Pumpengehäuse (6) axial unverschiebbar in dem saugseitigen Flanschdec­kel (2) gelagert ist und sich druckseitig über die kämmenden Laufspindeln (12) und um 90° versetzt di­rekt auf der Antriebsspindel (8) abstützt.4. Seal-free pump according to one of claims 1 to 3, characterized in that the pump housing (6) is axially immovable in the suction-side flange cover (2) and on the pressure side via the meshing spindles (12) and offset by 90 ° directly on the Drive spindle (8) supports. 5. Dichtungsfreie Pumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Antriebsspindel (8) eine axiale Durchgangsbohrung (17) und ein dazu achsgleiches Sicherheitsventil (22) unmittelbar im Saugraum (14) aufweist.5. Seal-free pump according to one of claims 1 to 4, characterized in that the drive spindle (8) has an axial through bore (17) and one Has axially aligned safety valve (22) directly in the suction chamber (14). 6. Dichtungsfreie Pumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß im saugseitigen Be­reich des Gehäuses (6) Bohrungen (21) derart angeord­net sind, daß druckseitiges Fördermedium auf Planflä­chen (19) der kämmenden Laufspindeln (12) wirkt.6. Seal-free pump according to one of claims 1 to 5, characterized in that in the suction-side area of the housing (6) bores (21) are arranged such that pressure-side medium on flat surfaces (19) of the meshing running spindles (12) acts. 7. Dichtungsfreie Pumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Rotor (5) im Aus­trittsbereich (23) der Pumpe mit einer die Pulsati­onsfrequenz der Pumpe je nach Teilung erhöhenden An­zahl von Durchströmöffnungen (24) versehen ist und im Austrittsbereich (23) eine anschließende Pulsations­dämpfungseinrichtung (25) angeordnet ist.7. Seal-free pump according to one of claims 1 to 6, characterized in that the rotor (5) in the outlet region (23) of the pump with a pulsation frequency of the pump depending on the division increasing number of flow openings (24) is provided and in the outlet region ( 23) a subsequent pulsation damping device (25) is arranged. 8. Dichtungsfreie Pumpe nach Anspruch 7, dadurch gekenn­zeichnet, daß die Pulsationsdämpfungseinrichtung (25) als Sieb entsprechender Maschenweite ausgebildet ist.8. A seal-free pump according to claim 7, characterized in that the pulsation damping device (25) is designed as a sieve of appropriate mesh size. 9. Dichtungsfreie Pumpe nach Anspruch 7, dadurch gekenn­zeichnet, daß die Durchströmöffnungen (24) zusätzlich mit das Fördermedium entsprechend einem Laufrad einer Strömungsmaschine beschleunigenden Profilierungen ausgestattet sind und im Austrittsbereich (23) die Pulsationsdämpfungseinrichtung als Leitradbeschaufe­lung ausgebildet ist.9. A seal-free pump according to claim 7, characterized in that the through-flow openings (24) are additionally equipped with the pumping medium corresponding to an impeller of a turbomachine accelerating profiles and in the outlet area (23) the pulsation damping device is designed as stator blades.
EP89100066A 1988-01-08 1989-01-04 Sealless pump Withdrawn EP0323834A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19883800336 DE3800336A1 (en) 1988-01-08 1988-01-08 SEAL-FREE PUMP
DE3800336 1988-01-08

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EP0323834A2 true EP0323834A2 (en) 1989-07-12
EP0323834A3 EP0323834A3 (en) 1990-02-14

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US4957417A (en) * 1989-07-14 1990-09-18 Kabushiki Kaisha Kobe Seiko Sho Vertical oilless screw vacuum pump
GB2340186A (en) * 1998-08-06 2000-02-16 Automotive Motion Tech Ltd A motor driven pump
WO2000008338A1 (en) * 1998-08-06 2000-02-17 Automotive Motion Technology Limited A motor driven pump
WO2001073295A1 (en) * 2000-03-29 2001-10-04 Voith Turbo Gmbh & Co. Kg Motor-pump unit
GB2401396A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump assembly
GB2401398A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump with output through central bore in journal bearing
USRE39597E1 (en) 2001-07-02 2007-05-01 Carrier Corporation Variable speed drive chiller system
WO2012161574A1 (en) * 2011-05-20 2012-11-29 J.G.M. Van Heck Beheer B.V. Pump, pump system and method for pumping a medium
WO2012058702A3 (en) * 2010-11-02 2013-05-10 Kral Ag Pump-out device for pumping mineral oil out of an oil tank
CN103758758A (en) * 2014-01-17 2014-04-30 西安交通大学 Alternating current servo direct drive electro-hydraulic pump
CN104033381A (en) * 2014-05-15 2014-09-10 西安交通大学 Alternating-current servo direct-drive type two-stage five-screw-rod electro-hydraulic pump
EP3163085A1 (en) 2015-10-27 2017-05-03 Kolektor Micro-Motor d.o.o. System consisting of an electromotor and working machine
WO2019002203A1 (en) * 2017-06-27 2019-01-03 Continental Automotive Gmbh Screw-spindle pump, fuel delivery assembly, and fuel delivery unit
EP3816419A1 (en) * 2019-10-31 2021-05-05 Illinois Tool Works Inc. Screw pump and a cooling circuit of a vehicle presenting such a pump
EP3832137A1 (en) * 2019-12-02 2021-06-09 Leistritz Pumpen GmbH Screw spindle pump

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DE3920901C2 (en) * 1989-06-26 1995-02-16 Allweiler Ag Screw pump
DE19949082B4 (en) * 1999-10-12 2006-03-02 Ti Automotive (Neuss) Gmbh Fuel pump for internal combustion engines
DE102018220811A1 (en) * 2018-12-03 2020-06-04 Audi Ag Device for conveying a cooling fluid

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FR1061407A (en) * 1952-08-12 1954-04-12 Driving machine combined with a working machine
US2924181A (en) * 1957-05-13 1960-02-09 Laval Steam Turbine Co Screw pumps or motors
US3263619A (en) * 1965-10-04 1966-08-02 Laval Turbine Motor-pump unit

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4957417A (en) * 1989-07-14 1990-09-18 Kabushiki Kaisha Kobe Seiko Sho Vertical oilless screw vacuum pump
US6499966B1 (en) 1998-08-06 2002-12-31 Automative Motion Technology, Ltd. Motor driven pump
GB2340186A (en) * 1998-08-06 2000-02-16 Automotive Motion Tech Ltd A motor driven pump
WO2000008338A1 (en) * 1998-08-06 2000-02-17 Automotive Motion Technology Limited A motor driven pump
GB2340186B (en) * 1998-08-06 2000-12-20 Automotive Motion Tech Ltd A motor driven pump
US6585498B2 (en) 2000-03-29 2003-07-01 Voith Turbo Gmbh & Co Kg Motor-pump unit with pump shaft pinion enmeshed with motor rotor
WO2001073295A1 (en) * 2000-03-29 2001-10-04 Voith Turbo Gmbh & Co. Kg Motor-pump unit
USRE39597E1 (en) 2001-07-02 2007-05-01 Carrier Corporation Variable speed drive chiller system
GB2401396A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump assembly
GB2401398A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump with output through central bore in journal bearing
EP1475538A2 (en) * 2003-05-08 2004-11-10 Automotive Motion Technology Limited Pump
EP1475538A3 (en) * 2003-05-08 2005-01-12 Automotive Motion Technology Limited Pump
WO2012058702A3 (en) * 2010-11-02 2013-05-10 Kral Ag Pump-out device for pumping mineral oil out of an oil tank
WO2012161574A1 (en) * 2011-05-20 2012-11-29 J.G.M. Van Heck Beheer B.V. Pump, pump system and method for pumping a medium
CN103547807A (en) * 2011-05-20 2014-01-29 吉格姆凡赫克比希尔公司 Pump, pump system and method for pumping a medium
US9587637B2 (en) 2011-05-20 2017-03-07 J.G.M. Van Heck Beheer B.V. Pump, pump system and method for pumping a medium
CN103758758A (en) * 2014-01-17 2014-04-30 西安交通大学 Alternating current servo direct drive electro-hydraulic pump
CN103758758B (en) * 2014-01-17 2015-11-25 西安交通大学 A kind of AC servo direct-driving type electricity liquid pump
CN104033381A (en) * 2014-05-15 2014-09-10 西安交通大学 Alternating-current servo direct-drive type two-stage five-screw-rod electro-hydraulic pump
CN104033381B (en) * 2014-05-15 2016-04-13 西安交通大学 A kind of AC servo direct-driving type secondary five screw rod electricity liquid pump
EP3163085A1 (en) 2015-10-27 2017-05-03 Kolektor Micro-Motor d.o.o. System consisting of an electromotor and working machine
WO2019002203A1 (en) * 2017-06-27 2019-01-03 Continental Automotive Gmbh Screw-spindle pump, fuel delivery assembly, and fuel delivery unit
CN110945244B (en) * 2017-06-27 2021-11-19 纬湃科技有限责任公司 Screw spindle pump, fuel delivery assembly and fuel delivery unit
US11306715B2 (en) 2017-06-27 2022-04-19 Vitesco Technologies GmbH Screw-spindle pump, fuel delivery assembly, and fuel delivery unit
EP3816419A1 (en) * 2019-10-31 2021-05-05 Illinois Tool Works Inc. Screw pump and a cooling circuit of a vehicle presenting such a pump
EP3832137A1 (en) * 2019-12-02 2021-06-09 Leistritz Pumpen GmbH Screw spindle pump
US11371501B2 (en) 2019-12-02 2022-06-28 Leistritz Pumpen Gmbh Screw spindle pump

Also Published As

Publication number Publication date
DE3800336A1 (en) 1989-07-27
EP0323834A3 (en) 1990-02-14
DE3800336C2 (en) 1990-05-31

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