EP0071715B1 - Liquid ring vacuum pump for gaseous fluids - Google Patents

Liquid ring vacuum pump for gaseous fluids Download PDF

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Publication number
EP0071715B1
EP0071715B1 EP82105132A EP82105132A EP0071715B1 EP 0071715 B1 EP0071715 B1 EP 0071715B1 EP 82105132 A EP82105132 A EP 82105132A EP 82105132 A EP82105132 A EP 82105132A EP 0071715 B1 EP0071715 B1 EP 0071715B1
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EP
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Prior art keywords
pressure
liquid
vacuum pump
liquid ring
rotor
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Expired
Application number
EP82105132A
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German (de)
French (fr)
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EP0071715A3 (en
EP0071715A2 (en
Inventor
Wilfried Lübke
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Siemens AG
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Siemens AG
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Publication of EP0071715A3 publication Critical patent/EP0071715A3/en
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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
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F04C19/005—Details concerning the admission or discharge
    • F04C19/007—Port members in the form of side plates

Definitions

  • the invention relates to a liquid vacuum pump for gaseous media with a machine housing which eccentrically surrounds an impeller and which is closed at the end by end shields for the impeller shaft, of which at least one end shield has separate inlets and outlets for the medium which pass through suction and pressure slots a plane control disc arranged between it and the machine housing with vane chambers of the impeller which are closed off from the circumference of the liquid ring, that a pressure fluid channel connected to an external pressure fluid supply line is provided in the end shield between its inlets and outlets and opens into a pressure fluid inlet provided in the control disc and the hydraulic fluid inlet corresponds to a hydraulic fluid passage located on the end face in front of the impeller hub below the shaft passage in the control disk, so that the hydraulic fluid seals the gap in the fluids tsring flows off.
  • Such vacuum pumps are from the Siemens price list P20, part I from July 1964, esp. Pages 4 to 7 and from the Siemens publication order no. E725 / 1013 "Vacuum pumps and compressors Siemens system ELMO-F " esp. Pages 2 to 5, known.
  • the known vacuum pumps each have a passage in the control disk for the supply of return liquid (also referred to as suction liquid or circulating liquid), which is removed from the liquid separator of the vacuum pump as part of the operating liquid replacing the loss in the rotating liquid ring.
  • return liquid also referred to as suction liquid or circulating liquid
  • the portion of the operating fluid required to cool the vacuum pump is supplied to the vacuum pump as fresh or recooled pressure fluid.
  • the pressure fluid can either be taken from water supply networks as fresh water or in a circuit from the liquid separator with the interposition of a heat exchanger and a pressure increasing device or from pressure-increasing scoop pipes arranged in the machine housing according to DE-A-2317 420.
  • gap losses occur in the known vacuum pumps in all operating modes up to an intake pressure of about 60 mbar, which impair the efficiency.
  • a reduction in the gap losses by reducing the axial play of the impellers can only be achieved to a very limited extent, since the operational safety of the vacuum pump is questioned if the axial play is too small.
  • liquid ring vacuum pumps of the type mentioned at the outset which are also intended to convey liquids in the region of higher suction pressures besides gaseous medium
  • this pre-separator requires a reduced efficiency when only gas is extracted.
  • the object of the invention is to make do without passages for the return liquid and without pressure-increasing devices in circular operation and, with a simpler design of the liquid ring vacuum pumps, to operate them with higher efficiency without erosion and / or cavitation damage.
  • the impeller (not shown) with blades arranged on the circumference of its impeller hub is arranged eccentrically in a machine housing (not shown).
  • the impeller shaft penetrates shaft passages 4 of plane control disks 1 covering the machine housing, for example on both sides, which are in turn covered on the outside by end shields (not shown) for the impeller shaft and which in the case of the described double-flow pump have separate inlets and outlets for the medium to be pumped.
  • These inlets or outlets are connected via suction slits 2 or pressure slits 3 in the control disks 1 to the vane chambers which are closed on the circumference by the liquid ring which rotates within the machine housing with the impeller.
  • Liquid channels are provided in the end shields between the inlets and outlets, which are connected to a hydraulic fluid supply line located outside the machine and open into hydraulic fluid inlets 5 to hydraulic fluid passages 6 in the control disks 1.
  • the pressure fluid passage 6 is formed on the side 1A as an annular groove surrounding the shaft passage 4, into which an inflow channel 7 attached on the side 1A opens from the outer circumference.
  • the inflow channel 7 deflects the gap-sealing pressure fluid in the direction of the rotating fluid ring into it in a vortex-free manner, the inflow channel 7, viewed in the direction of the impeller rotation, being arranged behind the suction slot 2 and below the shaft passage 4 parallel to a diameter axis running between the suction and pressure slot as a milling groove.
  • several inflow channels can also be provided.
  • a liquid ring vacuum pump is connected at the outlet of each end shield to a separator which is connected to the pressure fluid inlet 5 via a line (not shown) instead of, as is known, to a liquid return.

Description

Die Erfindung betrifft eine Flüssigkeits-Vakuumpumpe für gasförmige Medien mit einem ein Laufrad exzentrisch umgebenden Maschinengehäuse, das stirnseitig von Lagerschilden für die Laufradwelle abgeschlossen ist, von denen wenigstens ein Lagerschild getrennte Ein- und Auslässe für das Medium aufweist, die über Saug-und Druckschlitze in einer zwischen ihm und dem Maschinengehäuse angeordneten ebenen Steuerscheibe mit vom Flüssigkeitsring umfangsseitig abgeschlossenen Schaufelkammern des Laufrades in Verbindung stehen, daß im Lagerschild zwischen dessen Ein- und Auslässen ein an eine äußere Druckflüssigkeitszuleitung angeschlossener Druckflüssigkeitskanal vorgesehen ist, der in einem in der Steuerscheibe vorgesehenen Druckflüssigkeitseinlauf mündet und der Druckflüssigkeitseinlauf mit einem stirnseitig vor der Laufradnabe angeordneten Druckflüssigkeitsdurchlaß unterhalb des Wellendurchlasses in der Steuerscheibe korrespondiert, so daß die Druckflüssigkeit spaltabdichtend in den Flüssigkeitsring abfließt.The invention relates to a liquid vacuum pump for gaseous media with a machine housing which eccentrically surrounds an impeller and which is closed at the end by end shields for the impeller shaft, of which at least one end shield has separate inlets and outlets for the medium which pass through suction and pressure slots a plane control disc arranged between it and the machine housing with vane chambers of the impeller which are closed off from the circumference of the liquid ring, that a pressure fluid channel connected to an external pressure fluid supply line is provided in the end shield between its inlets and outlets and opens into a pressure fluid inlet provided in the control disc and the hydraulic fluid inlet corresponds to a hydraulic fluid passage located on the end face in front of the impeller hub below the shaft passage in the control disk, so that the hydraulic fluid seals the gap in the fluids tsring flows off.

Solche Vakuumpumpen sind aus der Siemens-Preisliste P20, I. Teil vom Juli 1964, insb. Seiten 4 bis 7 sowie aus der Siemens Druckschrift Best. Nr. E725/1013 «Vakuumpumpen und Verdichter Siemens-System ELMO-F" insb. Seiten 2 bis 5, bekannt.Such vacuum pumps are from the Siemens price list P20, part I from July 1964, esp. Pages 4 to 7 and from the Siemens publication order no. E725 / 1013 "Vacuum pumps and compressors Siemens system ELMO-F " esp. Pages 2 to 5, known.

Die bekannten Vakuumpumpen haben in der Steuerscheibe jeweils einen Durchlaß für die Zuführung von Rücklaufflüssigkeit (auch als Saugflüssigkeit bzw. Umlaufflüssigkeit bezeichnet), die als ein Teil der den Verlust im rotierenden Flüssigkeitsring ersetzenden Betriebsflüssigkeit aus dem Flüssigkeitsabscheider der Vakuumpumpe entnommen wird. Im Bereich dieser Durchlässe der Steuerscheiben treten an den Steuerscheiben und den Laufrädern merkliche Erosions- und/oder Kavitationsschäden auf, die auch durch Verwendung von hochwertigem CrNi-Stahl für diese Maschinenteile auf die Dauer nicht verhindert werden können. Der zur Kühlung der Vakuumpumpe benötigte Anteil der Betriebsflüssigkeit wird als frische oder rückgekühlte Druckflüssigkeit der Vakuumpumpe zugeführt.The known vacuum pumps each have a passage in the control disk for the supply of return liquid (also referred to as suction liquid or circulating liquid), which is removed from the liquid separator of the vacuum pump as part of the operating liquid replacing the loss in the rotating liquid ring. In the area of these passages of the control disks, noticeable erosion and / or cavitation damage occurs on the control disks and the impellers, which cannot be prevented in the long term even by using high-quality CrNi steel for these machine parts. The portion of the operating fluid required to cool the vacuum pump is supplied to the vacuum pump as fresh or recooled pressure fluid.

Die Druckflüssigkeit kann entweder aus Wasserversorgungsnetzen als Frischwasser oder im Kreisbetrieb aus dem Flüssigkeitsabscheider unter Zwischenschaltung eines Wärmetauschers und einer Druckerhöhungsvorrichtung oder von im Maschinengehäuse gemäß DE-A-2317 420 angeordneten druckerhöhenden Schöpfrohren entnommen werden.The pressure fluid can either be taken from water supply networks as fresh water or in a circuit from the liquid separator with the interposition of a heat exchanger and a pressure increasing device or from pressure-increasing scoop pipes arranged in the machine housing according to DE-A-2317 420.

Bei Verwendung von solchen gesonderte Druckerhöhungspumpen ersetzenden Schöpfrohren können im Bereich der Schöpfrohre ebenfalls Erosionsschäden auftreten.When using such separate scoop pipes replacing pressure booster pumps, erosion damage can also occur in the area of the scoop pipes.

Darüberhinaus treten bei den bekannten Vakuumpumpen bei sämtlichen Betriebsarten bis etwa 60 mbar Ansaugdruck Spaltverluste auf, die den Wirkungsgrad verschlechtern. Eine Herabsetzung der Spaltverluste durch Verkleinerung der Axialspiele der Laufräder läßt sich nur sehr begrenzt verwirklichen, da bei zu kleinem Axialspiel die Betriebssicherheit der Vakuumpumpe in Frage gestellt ist.In addition, gap losses occur in the known vacuum pumps in all operating modes up to an intake pressure of about 60 mbar, which impair the efficiency. A reduction in the gap losses by reducing the axial play of the impellers can only be achieved to a very limited extent, since the operational safety of the vacuum pump is questioned if the axial play is too small.

Bei Flüssigkeitsring-Vakuumpumpen der eingangs genannten Art, die im Bereich höherer Ansaugdrücke außer gasförmigem Medium auch Flüssigkeiten fördern sollen, ergäbe sich ein erhöhter Leistungsbedarf und eine Verschlechterung der Laufeigenschaften im Sinne einer beschleunigten Abnutzung der Lager des Laufrades, wenn nicht in die Saugleitung vor der Vakuumpumpe ein gesonderter Vorabscheider eingebaut würde, der die Flüssigkeit vom gasförmigen Medium vor der Vakuumpumpe absondert. Dieser Vorabscheider bedingt aber bei ausschließlicher Gasförderung einen verminderten Wirkungsgrad.With liquid ring vacuum pumps of the type mentioned at the outset, which are also intended to convey liquids in the region of higher suction pressures besides gaseous medium, there would be an increased power requirement and a deterioration in the running properties in the sense of accelerated wear of the bearings of the impeller, if not in the suction line in front of the vacuum pump a separate pre-separator would be installed, which separates the liquid from the gaseous medium in front of the vacuum pump. However, this pre-separator requires a reduced efficiency when only gas is extracted.

Aufgabe der Erfindung ist es, ohne Durchlässe für die Rücklaufflüssigkeit sowie ohne Druckerhöhungsvorrichtungen bei Kreisbetrieb auszukommen und bei einfacherer Ausführung der Flüssigkeitsring-Vakuumpumpen diese mit höherem Wirkungsgrad ohne Erosions- und/oder Kavitaionsschäden zu betreiben.The object of the invention is to make do without passages for the return liquid and without pressure-increasing devices in circular operation and, with a simpler design of the liquid ring vacuum pumps, to operate them with higher efficiency without erosion and / or cavitation damage.

Die Lösung der gestellten Aufgabe gelingt durch die kennzeichnenden Merkmale des Patentanspruches 1.The problem is solved by the characterizing features of claim 1.

Bei Pumpenbetrieb im höheren Bereich der Ansaugdrücke unter Mitförderung von Flüssigkeit gelingt es, darüberhinaus, ohne Vorabscheider in der Saugleitung eine Verringerung der Leistungsaufnahme unter verbessereten Laufeigenschaften bzw. ohne Mitförderung von ...In pump operation in the higher range of the suction pressures with the conveyance of liquid, it is moreover possible, without a pre-separator in the suction line, to reduce the power consumption with improved running properties or without the conveyance of ...

Betriebsflüssigkeit eine Verbesserung des Wirkungsgrades zu erhalten, durch die kennzeichnenden Merkmale des Patentanspruchs 3.Operating fluid to obtain an improvement in efficiency by the characterizing features of claim 3.

Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand von zusätzlichen Unteransprüchen.Advantageous embodiments of the invention are the subject of additional subclaims.

Ein Ausführungsbeispiel einer erfindungsgemäß verbesserten Steuerscheibe für eine Flüssigkeitsring-Vakuumpumpe der eingangs genannten Art ist anhand der Zeichnung nachfolgend näher erläutert. Es zeigt

  • Figur 1 die Draufsicht auf die dem Lagerschild mit Ein- und Auslaß zugewandte Seite der Steuerscheibe und
  • Figur 2 die Draufsicht auf die dem Läuferrad zugewandte Seite der Steuerscheibe.
An embodiment of an improved control disk according to the invention for a liquid ring vacuum pump of the type mentioned is explained in more detail below with reference to the drawing. It shows
  • 1 shows the top view of the side of the control disk facing the end shield with inlet and outlet and
  • Figure 2 is a plan view of the side of the control disc facing the rotor.

Bei Flüssigkeitsring-Vakuumpumpen der hier in Betracht gezogenen Art ist das nicht dargestellte Laufrad mit am Umfang seiner Laufradnabe angeordneten Schaufeln exzentrisch in einem nicht dargestellten Maschinengehäuse angeordnet. Die Laufradwelle durchdringt Wellendurchlässe 4 von das Maschinengehäuse beispielsweise beidseitig abdeckenden ebenen Steuerscheiben 1, die ihrerseits nach außen von nicht dargestellten Lagerschilden für die Laufradwelle abgedeckt sind und die im Falle der geschilderten doppelflutigen Pumpe jeweils getrennte Ein- und Auslässe für das zu fördernde Medium haben. Diese Einlässe bzw. Auslässe stehen über Saugschlitze 2 bzw. Druckschlitze 3 in den Steuerscheiben 1 mit den vom innerhalb des Maschinengehäuses mit dem Flügelrad mitrotierenden Flüssigkeitsring umfangsseitig abgeschlossenen Schaufelkammern in Verbindung. In den Lagerschilden sind zwischen den Einlässen und Auslässen jeweils Flüssigkeitskanäle vorgesehen, die mit einer außerhalb der Maschine befindlichen Druckflüssigkeitszuleitung verbunden sind und in Druckflüssigkeitseinläufe 5 zu Druckflüssigkeitsdurchlässen 6 in den Steuerscheiben 1 münden.In liquid ring vacuum pumps of the type under consideration here, the impeller (not shown) with blades arranged on the circumference of its impeller hub is arranged eccentrically in a machine housing (not shown). The impeller shaft penetrates shaft passages 4 of plane control disks 1 covering the machine housing, for example on both sides, which are in turn covered on the outside by end shields (not shown) for the impeller shaft and which in the case of the described double-flow pump have separate inlets and outlets for the medium to be pumped. These inlets or outlets are connected via suction slits 2 or pressure slits 3 in the control disks 1 to the vane chambers which are closed on the circumference by the liquid ring which rotates within the machine housing with the impeller. Liquid channels are provided in the end shields between the inlets and outlets, which are connected to a hydraulic fluid supply line located outside the machine and open into hydraulic fluid inlets 5 to hydraulic fluid passages 6 in the control disks 1.

Der Druckflüssigkeitsdurchlaß 6 ist auf der Seite 1A als eine den Wellendurchlaß 4 umgebende Ringnut ausgebildet, in die vom äußeren Umfang her eine auf der Seite 1A angebrachte Einströmrinne 7 mündet. Die Einströmrinne 7 lenkt die spaltabdichtende Druckflüssigkeit in Richtung des rotierenden Flüssigkeitsringes in diesen wirbelfrei ein, wobei die Einströmrinne 7 in Laufraddrehrichtung gesehen hinter dem Saugschlitz 2 und unterhalb des Wellendurchlasses 4 parallel zu einer zwischen Saug- und Druckschlitz verlaufenden Durchmesserachse als Fräsnut angebracht ist. Unter Umständen können auch mehrere Einströmrinnen vorgesehen sein.The pressure fluid passage 6 is formed on the side 1A as an annular groove surrounding the shaft passage 4, into which an inflow channel 7 attached on the side 1A opens from the outer circumference. The inflow channel 7 deflects the gap-sealing pressure fluid in the direction of the rotating fluid ring into it in a vortex-free manner, the inflow channel 7, viewed in the direction of the impeller rotation, being arranged behind the suction slot 2 and below the shaft passage 4 parallel to a diameter axis running between the suction and pressure slot as a milling groove. Under certain circumstances, several inflow channels can also be provided.

In vielen Fällen ist eine Flüssigkeitsring-Vakuumpumpe am Auslaß jedes Lagerschildes mit einem Abscheider verbunden, der über eine nicht dargestellte Leitung mit dem Druckflüssigkeitseinlauf 5 verbunden ist, statt wie bekannterweise mit einem Flüssigkeitsrücklauf.In many cases, a liquid ring vacuum pump is connected at the outlet of each end shield to a separator which is connected to the pressure fluid inlet 5 via a line (not shown) instead of, as is known, to a liquid return.

Bei Wegfall eines Abscheiders ist dagegen der Sumpf der Maschine mit dem Druckflüssigkeitseinlauf 5 zu verbinden.If there is no separator, however, the sump of the machine must be connected to the pressure fluid inlet 5.

Mit einer solchen Vakuumpumpe können bei niedrigen Ansaugdrücken bis etwa 60 mbar im Kreisbetrieb ohne erosionsgefährdete Schöpfröhre und ohne gesonderte Druckerhöhungspumpen größere Ansaugvolumenströme unter Verringerr.ng der Spaltverluste und mit besserem Wirkungsgrad gefördert werden, wobei die äußere Betriebsflüssigkeitsführung vereinfacht ist. Außerdem können die sonst im Bereich von « Umlaufflüssigkeitsbohrungen der Steuerscheiben auftretenden Erosionsschäden durch den Wegfall solcher Umlaufflüssigkeitsbohrungen infolge Wegfalls der Saugflüssigkeitsleitung erst gar nicht auftreten.With such a vacuum pump, large suction volume flows can be promoted at low suction pressures of up to about 60 mbar in circular operation without a scoop tube at risk of erosion and without separate pressure booster pumps, while reducing the gap losses and with better efficiency, whereby the external operating fluid flow is simplified. In addition, the erosion damage that otherwise occurs in the area of “circulating fluid bores of the control disks due to the omission of such circulating fluid bores as a result of the omission of the suction fluid line cannot even occur.

Bei Vakuumpumpen, die im Bereich höherer Ansaugdrücke etwa ab 180 mbar arbeiten, ist eine Verbesserung des Wirkungsgrades ohne Mitförderung von Flüssigkeiten bzw. eine Verbesserung der Laufeigenschaften und eine Verminderung des Leistungsgedarfes bei Mitförderung von Flüssigkeiten durch die Anbringung von zusätzlichen Entlastungsdurchlässen 8 in den Steuerscheiben 1 erreichbar.In the case of vacuum pumps which operate in the range of higher intake pressures of approximately 180 mbar, an improvement in the efficiency without the conveyance of liquids or an improvement in the running properties and a reduction in the power requirement for the conveyance of liquids can be achieved by attaching additional relief passages 8 in the control disks 1 .

Jeweils oberhalb des Druckschlitzes 3, getrennt von diesem, ist dessen Außenkontur benachbart ein Entlastungsdurchlaß 8 als Bohrung oberhalb des Druckschlitzendes angeordnet, der bei Mitförderung von Flüssigkeit vom rotierenden Flüssigkeitsring überdeckt wird.Each above the pressure slot 3, separated from it, the outer contour of which is arranged adjacent to a relief passage 8 as a bore above the end of the pressure slot, which is covered by the rotating liquid ring when liquid is carried along.

Claims (4)

1. Liquid ring vacuum pump for gaseous media having a machine housing eccentrically enclosing a rotor, which housing is closed off on its frontal face by bearing plates for the rotor shaft, of which bearing plates at least one has separate inlets and outlets for the medium, which are linked to blade chambers of the rotor closed off on the peripheral side by the liquid ring by means of suction slots (2) and pressure slots (3) in a plane control disc (1) arranged between it and the machine housing, that in the bearing plate between its inlets and outlets there is provided a pressure liquid channel connected to an external pressure liquid supply line, which channel opens into a pressure liquid inlet (5) provided in the control disc (1), and the pressure liquid inlet (5) corresponds with a pressure liquid discharge opening (6) arranged on the frontal face in front of the rotor hub and below the shaft aperture (4) in the control disc (1), so that the pressure liquid flows into the liquid ring sealing off any gaps, characterised in that the control disc (1) has on the side (1A) facing the rotor at least one inflow channel (7), seen in the direction of rotation of the rotor behind the suction slot (2) and below the shaft aperture (4), which channel extends over the rotor hub area into the blade chamber area, and is connected to the pressure liquid discharge opening (6), and a liquid filter subsequently connected to the outlet in the bearing plate, or, when there is no liquid filter, the sump of the vacuum pump, is connected exclusively to the pressure liquid supply line.
2. Liquid ring vacuum pump according to claim 1, characterised in that a single intake channel (7) is arranged in longitudinal extension parallel to a diametral axis of the control disc (1) lying between the suction- and pressure-slot (2, 3), and is in the form of a milled groove.
3. Liquid ring-vacuum pump for gaseous media according to claim 1 or 2 for the optional simultaneous conveyance of liquids, characterised in that the control disc (1) has, above the pressure slot (3) and adjacent to its outer edge, at least one additional discharge outlet (8) for the liquid ring separate from the pressure slot (3).
4. Liquid ring-vacuum pump according to claim 3, characterised in that the discharge outlet (8) is provided as a bore above the end of the pressure slot.
EP82105132A 1981-06-24 1982-06-11 Liquid ring vacuum pump for gaseous fluids Expired EP0071715B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3124867A DE3124867C2 (en) 1981-06-24 1981-06-24 Liquid ring vacuum pump for gaseous media
DE3124867 1981-06-24

Publications (3)

Publication Number Publication Date
EP0071715A2 EP0071715A2 (en) 1983-02-16
EP0071715A3 EP0071715A3 (en) 1984-03-07
EP0071715B1 true EP0071715B1 (en) 1986-09-10

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ID=6135297

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EP82105132A Expired EP0071715B1 (en) 1981-06-24 1982-06-11 Liquid ring vacuum pump for gaseous fluids

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US (1) US4545730A (en)
EP (1) EP0071715B1 (en)
JP (1) JPS585495A (en)
AU (1) AU552788B2 (en)
BR (1) BR8203646A (en)
CA (1) CA1217173A (en)
DE (1) DE3124867C2 (en)
IN (1) IN160801B (en)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3337837A1 (en) * 1983-10-18 1985-04-25 Siemens AG, 1000 Berlin und 8000 München LIQUID RING PUMP
US4521161A (en) * 1983-12-23 1985-06-04 The Nash Engineering Company Noise control for conically ported liquid ring pumps
US4551070A (en) * 1983-12-23 1985-11-05 The Nash Engineering Company Noise control for conically ported liquid ring pumps
JPS6220445U (en) * 1985-07-23 1987-02-06
US4756672A (en) * 1986-01-27 1988-07-12 Siemens Aktiengesellschaft Liquid-ring pump with maintenance of liquid level
US4755107A (en) * 1986-05-14 1988-07-05 Siemens Aktiengesellschaft Liquid-ring pump having additional openings in control disc for warm and cold liquid
US4679987A (en) * 1986-05-19 1987-07-14 The Nash Engineering Company Self-priming liquid ring pump methods and apparatus
DE4214960C1 (en) * 1992-05-06 1993-11-25 Siemens Ag Liquid ring machine
DE4301907A1 (en) * 1993-01-25 1994-07-28 Siemens Ag Liquid ring machine
US5464329A (en) * 1994-05-25 1995-11-07 Miura Co., Ltd. Water ring type pump with sidewall water reflux passage
GB2303879B (en) * 1995-08-01 1999-09-15 Hick Hargreaves & Co Ltd Liquid ring pump
CN1079503C (en) * 1995-08-16 2002-02-20 西门子公司 Ring liquid compression engine
US6106239A (en) * 1997-11-14 2000-08-22 Vooner Vacuum Pumps, Inc. Air flow apparatus for liquid ring vacuum pump
DE29803322U1 (en) * 1998-02-25 1999-07-15 Speck Pumpen Walter Speck Kg Liquid ring machine
US6558131B1 (en) * 2001-06-29 2003-05-06 nash-elmo industries, l.l.c. Liquid ring pumps with automatic control of seal liquid injection
ATE404793T1 (en) * 2006-05-11 2008-08-15 Pompetravaini S P A SINGLE-STAGE LIQUID RING VACUUM PUMP WITH SUCTION AND PRESSURE LINES INTEGRATED IN THE CENTRAL HOUSING.
JP6151710B2 (en) * 2011-11-22 2017-06-21 ステアリング・インダストリー・コンサルト・ゲゼルシャフト・ミット・ベシュレンクテル・ハフツングＳｔｅｒｌｉｎｇ Ｉｎｄｕｓｔｒｙ Ｃｏｎｓｕｌｔ ＧｍｂＨ Impeller for liquid ring vacuum pump and liquid ring vacuum pump
US9689387B2 (en) * 2012-10-30 2017-06-27 Gardner Denver Nash, Llc Port plate of a flat sided liquid ring pump having a gas scavenge passage therein

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2317420A1 (en) * 1973-04-06 1975-03-13 Siemens Ag LIQUID RING GAS COMPRESSORS

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US29747A (en) * 1860-08-21 Improved telegraphic instrument
AT63355B (en) * 1912-08-26 1914-02-10 Siemens Schuckertwerke Wien Impeller fan or pump with eccentric housing and sealing circular liquid ring.
US1180613A (en) * 1913-03-19 1916-04-25 Siemens Schuckertwerke Gmbh Rotary pump.
US1662250A (en) * 1926-06-11 1928-03-13 Irving C Jennings Method and apparatus relating to motor-driven pumps
DE1027358B (en) * 1955-02-08 1958-04-03 Siemens Ag Liquid ring pump
GB1284473A (en) * 1969-04-26 1972-08-09 Siemens Ag Improvements in or relating to liquid ring pumps
DE2318538B2 (en) * 1973-04-12 1975-12-04 Siemens Ag, 1000 Berlin Und 8000 Muenchen Distributor for a liquid ring gas compressor
DE2541050B2 (en) * 1975-09-15 1977-09-29 Siemens AG, 1000 Berlin und 8000 München LIQUID RING COMPRESSORS
US4273515A (en) * 1976-04-07 1981-06-16 General Signal Corporation Liquid ring pump
US4323334A (en) * 1980-01-25 1982-04-06 The Nash Engineering Company Two stage liquid ring pump
US4392783A (en) * 1980-12-12 1983-07-12 The Nash Engineering Company Liquid ring pump employing discharged pumping liquid for discharge port control

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2317420A1 (en) * 1973-04-06 1975-03-13 Siemens Ag LIQUID RING GAS COMPRESSORS

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
SIEMENS DRUCKSCHRIFT Best. Nr. E725/1013 *
SIEMENS-PREISLISTE P 20(I.Teil) *

Also Published As

Publication number Publication date
IN160801B (en) 1987-08-08
JPS585495A (en) 1983-01-12
DE3124867A1 (en) 1983-01-13
EP0071715A3 (en) 1984-03-07
AU552788B2 (en) 1986-06-19
BR8203646A (en) 1983-06-14
EP0071715A2 (en) 1983-02-16
DE3124867C2 (en) 1983-11-17
AU8514682A (en) 1983-01-06
US4545730A (en) 1985-10-08
CA1217173A (en) 1987-01-27

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