EP0758717A1 - Liquid ring compressor - Google Patents

Liquid ring compressor Download PDF

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Publication number
EP0758717A1
EP0758717A1 EP96112554A EP96112554A EP0758717A1 EP 0758717 A1 EP0758717 A1 EP 0758717A1 EP 96112554 A EP96112554 A EP 96112554A EP 96112554 A EP96112554 A EP 96112554A EP 0758717 A1 EP0758717 A1 EP 0758717A1
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EP
European Patent Office
Prior art keywords
impeller
pressure
liquid ring
distributor groove
operating fluid
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.)
Granted
Application number
EP96112554A
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German (de)
French (fr)
Other versions
EP0758717B1 (en
Inventor
Georg Dipl.-Ing. Plescher
Robert Dipl.-Ing. Siebenwurst
Bernhard Dipl.-Ing. Tews
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Siemens AG
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Siemens AG
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Publication date
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Publication of EP0758717A1 publication Critical patent/EP0758717A1/en
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Publication of EP0758717B1 publication Critical patent/EP0758717B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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

Definitions

  • the invention relates to a liquid ring compressor according to the preamble of claim 1.
  • Such a liquid ring compressor is known from DE-B-1027 358.
  • this compressor with respect to the direction of rotation of the impeller, an opening is provided directly after the pressure slot, which opening is connected in terms of flow to a radial transverse groove formed in the control disk.
  • the transverse groove in turn opens into an inner and an outer circumferential distributor groove.
  • operating fluid is conducted into the transverse groove and via this into the distributor grooves. From there, the operating fluid flows through the axial gap between the control disc and the impeller hub and thus seals it.
  • the pressure curve increases from the intake pressure to the compressor pressure over the circumference of the distributor groove.
  • the pressure difference between the supply pressure of the operating fluid and the pressure in the individual impeller cells is therefore not constant. As a result, more operating fluid is forced through the axial gap in areas with a higher pressure difference than in an area where the pressure difference is less high. This does not guarantee an even seal of the axial gap.
  • the invention has for its object to develop a liquid ring compressor of the generic type so that the sealing of the existing between the control disc and the impeller hub is significantly improved.
  • the problem is solved by the features specified in the characterizing part of claim 1.
  • the described arrangement of a blocking member in the distributor groove prevents a greater outflow of the operating fluid which seals the axial gap and is directed from the feed opening to the region of the greater pressure difference.
  • the operating fluid is guided much more by the arrangement of the blocking member on the corresponding side of the supply opening to the area where the pressure difference between the supply pressure of the operating fluid and the pressure in the impeller cells is less great. This results in an overall better distribution of the operating fluid sealing the axial gap over the full circumference of the distributor groove.
  • a direct flow from the supply opening to the area of the larger pressure difference can be completely prevented if the blocking member extends over the full radial height of the distributor groove.
  • the feed opening is provided in relation to the direction of rotation of the impeller in the area lying between the end of the suction slot and the beginning of the pressure slot.
  • the direction of flow of the operating fluid in the distributor groove coincides with the direction of rotation of the impeller, so that the operating fluid in the distributor groove is still carried along in the circumferential direction by the rotating impeller.
  • the compressor housing of a liquid ring compressor is designated by 1.
  • an intake port 2 opening into a suction chamber of the side plate attached to the housing and a pressure port 3 connected to a pressure chamber of the side plate.
  • Attached to the compressor housing 1 is a control disk 5 which separates the working chamber containing the impeller 4 of the compressor from the suction and pressure chamber of the side plate.
  • the impeller lying axially in front of the control disk 5 is indicated in dashed lines in the drawing.
  • the impeller 4 is offset with its axis of rotation 6 eccentrically with respect to the center axis of the compressor housing 1.
  • a radially adjacent to the shaft 8 of the impeller 4 to the hub 9 of the impeller 4 open distributor groove 10 is formed.
  • the distributor groove 10 extends over the full circumference of the impeller shaft 8.
  • a feed opening 11 opens into the distributor groove 10.
  • This feed opening 11 is, as can be seen from FIG. 2, in connection with a space 12 of the side plate filled with operating fluid. Operating fluid can thus flow into the distributor groove 10 via the feed opening 11. From the distributor groove 10, the operating fluid flows, as indicated by arrows 13, through the axial gap 14 existing between the control disk 5 and the impeller hub 9 into the working space of the compressor and mixes with the operating fluid forming the liquid ring in the working space. The operating fluid flowing through the axial gap 14 seals this gap.
  • the feed opening 11 is arranged in the region between the end of the suction slot 16 and the beginning of the pressure slot 17 of the control disk 5 with reference to the direction of rotation of the impeller 4 indicated by a rotating arrow 15.
  • a locking member which is designed as a finger 18 and projects radially inward into the distributor groove 10.
  • the finger 18 extends radially to the impeller shaft 8 and in the axial direction over the full depth of the distributor groove 10.
  • the distributor groove on the side towards the suction slot 16 is thus practically completely closed. On this side there is the greatest pressure difference between the operating fluid supplied and the pressure in the impeller cells rotating past the suction slot.
  • the distributor groove 10 is completely shut off by the finger 18, the operating liquid flowing into the distributor groove 10 via the feed opening 11 cannot flow directly to the region of the distributor groove adjacent to the suction slot 16. Rather, the operating fluid must flow through the distributor groove in the direction indicated by arrows 19. When flowing through the distributor groove 10, part of the operating fluid also flows radially outward through the axial gap 14 and seals it.

Abstract

The compressor has a housing (1) enclosing an eccentric impeller (4), with a control disc (5) on at least one side of the impeller. The control disc has suction and pressure slits (16,17) for supplying the compressed medium to and from the working chamber. A distributor channel (10) is provided within a region enclosed radially by the hub of the impeller, with a feed opening (11) for supplying a sealing fluid. At the side of the feed opening, where the higher pressure difference between the feed pressure of the operating fluid and the pressure in the impeller cells prevails, a blocking element is provided which projects radially into the distributor nut.

Description

Die Erfindung bezieht sich auf einen Flüssigkeitsringverdichter gemäß dem Oberbegriff des Anspruches 1.The invention relates to a liquid ring compressor according to the preamble of claim 1.

Ein solcher Flüssigkeitsringverdichter ist durch die DE-B-1027 358 bekannt. Bei diesem Verdichter ist in Bezug auf die Drehrichtung des Laufrades direkt nach dem Druckschlitz eine Öffnung vorgesehen, die strömungsmäßig mit einer in der Steuerscheibe ausgebildeten radialen Quernut verbunden ist. Die Quernut mündet ihrerseits in eine innere und eine äußere umlaufende Verteilernut. Durch die Öffnung, welche aufgrund ihrer räumlichen Lage von dem Flüssigkeitsring des Verdichters überdeckt ist, wird Betriebsflüssigkeit in die Quernut und über diese in die Verteilernuten geleitet. Von dort strömt die Betriebsflüssigkeit durch den zwischen der Steuerscheibe und der Laufradnabe bestehenden Axialspalt und dichtet diesen somit ab. Über den Umfang der Verteilernut ergibt sich ein vom Ansaugdruck bis zum Verdichterdruck ansteigender Druckverlauf. Somit ist der Druckunterschied zwischen dem Zuführdruck der Betriebsflüssigkeit und dem Druck in den einzelnen Laufradzellen nicht konstant. Dies führt dazu, daß in Bereichen eines höheren Druckunterschiedes folglich mehr Betriebsflüssigkeit durch den Axialspalt gedrückt wird, als in einem Bereich, wo der Druckunterschied weniger hoch ist. Damit ist keine gleichmäßige Abdichtung des Axialspaltes gewährleistet.Such a liquid ring compressor is known from DE-B-1027 358. In this compressor, with respect to the direction of rotation of the impeller, an opening is provided directly after the pressure slot, which opening is connected in terms of flow to a radial transverse groove formed in the control disk. The transverse groove in turn opens into an inner and an outer circumferential distributor groove. Through the opening, which is covered by the liquid ring of the compressor due to its spatial position, operating fluid is conducted into the transverse groove and via this into the distributor grooves. From there, the operating fluid flows through the axial gap between the control disc and the impeller hub and thus seals it. The pressure curve increases from the intake pressure to the compressor pressure over the circumference of the distributor groove. The pressure difference between the supply pressure of the operating fluid and the pressure in the individual impeller cells is therefore not constant. As a result, more operating fluid is forced through the axial gap in areas with a higher pressure difference than in an area where the pressure difference is less high. This does not guarantee an even seal of the axial gap.

Der Erfindung liegt die Aufgabe zugrunde, einen Flüssigkeitsringverdichter der gattungsgemäßen Art so weiterzubilden, daß die Abdichtung des zwischen der Steuerscheibe und der Laufradnabe bestehenden Axialspaltes deutlich verbessert ist.The invention has for its object to develop a liquid ring compressor of the generic type so that the sealing of the existing between the control disc and the impeller hub is significantly improved.

Die Lösung der gestellten Aufgabe gelingt durch die im Kennzeichen des Anspruches 1 angegebenen Merkmale. Durch die beschriebene Anordnung eines Sperrgliedes in der Verteilernut wird ein von der Zuführöffnung zu dem Bereich des größeren Druckunterschiedes gerichtetes stärkeres Abströmen der den Axialspalt abdichtenden Betriebsflüssigkeit verhindert. Die Betriebsflüssigkeit wird durch die Anordnung des Sperrgliedes auf der entsprechenden Seite der Zuführöffnung viel mehr zu dem Bereich gelenkt, wo der Druckunterschied zwischen Zuführdruck der Betriebsflüssigkeit und dem Druck in den Laufradzellen weniger groß ist. Damit ergibt sich über den vollen Umfang der Verteilernut eine insgeamt bessere Verteilung der den Axialspalt abdichtenden Betriebsflüssigkeit.The problem is solved by the features specified in the characterizing part of claim 1. The described arrangement of a blocking member in the distributor groove prevents a greater outflow of the operating fluid which seals the axial gap and is directed from the feed opening to the region of the greater pressure difference. The operating fluid is guided much more by the arrangement of the blocking member on the corresponding side of the supply opening to the area where the pressure difference between the supply pressure of the operating fluid and the pressure in the impeller cells is less great. This results in an overall better distribution of the operating fluid sealing the axial gap over the full circumference of the distributor groove.

Eine direkte Strömung von der Zuführöffnung zu dem Bereich des größeren Druckunterschiedes läßt sich vollständig verhindern, wenn sich das Sperrglied über die volle radiale Höhe der Verteilernut erstreckt.A direct flow from the supply opening to the area of the larger pressure difference can be completely prevented if the blocking member extends over the full radial height of the distributor groove.

Dadurch, daß die Verteilernut radial unmittelbar an die Welle des Laufrades angrenzt, ergibt sich eine maximale radiale Länge der Abdichtstrecke.Because the distributor groove radially adjoins the shaft of the impeller, there is a maximum radial length of the sealing section.

Besonders vorteilhaft ist es, daß die Zuführöffnung in Bezug auf die Drehrichtung des Laufrades in dem zwischen dem Ende des Saugschlitzes und dem Beginn des Druckschlitzes liegenden Bereich vorgesehen ist. In diesem Falle stimmt die Strömungsrichtung der Betriebsflüssigkeit in der Verteilernut mit der Drehrichtung des Laufrades überein, so daß die Betriebsflüssigkeit in der Verteilernut durch das rotierende Laufrad noch in Umfangsrichtung mitgenommen wird.It is particularly advantageous that the feed opening is provided in relation to the direction of rotation of the impeller in the area lying between the end of the suction slot and the beginning of the pressure slot. In this case, the direction of flow of the operating fluid in the distributor groove coincides with the direction of rotation of the impeller, so that the operating fluid in the distributor groove is still carried along in the circumferential direction by the rotating impeller.

Anhand des in der Zeichnung dargestellten Ausführungsbeispieles wird die Erfindung nachfolgend näher beschrieben. Es zeigt:

FIG 1
einen Flüssigkeitsringverdichter im Querschnitt mit einer Draufsicht auf die Steuerscheibe
FIG 2
in vergrößerter Darstellung einen Teillängsschnitt eines Flüssigkeitsringverdichters im Bereich der Steuerscheibe.
Based on the embodiment shown in the drawing, the invention is described in more detail below. It shows:
FIG. 1
a liquid ring compressor in cross section with a plan view of the control disc
FIG 2
an enlarged representation of a partial longitudinal section of a liquid ring compressor in the area of the control disk.

Mit 1 ist das Verdichtergehäuse eines Flüssigkeitsringverdichters bezeichnet. An dem Gehäuse 1 ist ein in einen Ansaugraum des am Gehäuse angebauten Seitenschildes mündender Ansaugstutzen 2 und ein mit einem Druckraum des Seitenschildes verbundener Druckstutzen 3 vorgesehen. An das Verdichtergehäuse 1 ist eine den das Laufrad 4 des Verdichters enthaltenden Arbeitsraum von dem Ansaug- und Druckraum des Seitenschildes trennende Steuerscheibe 5 angebaut. Das Axial vor der Steuerscheibe 5 liegende Laufrad ist in der Zeichnung gestrichelt angedeutet. Das Laufrad 4 ist mit seiner Drehachse 6 exzentrisch gegenüber der Mittenachse des Verdichtergehäuses 1 versetzt.The compressor housing of a liquid ring compressor is designated by 1. Provided on the housing 1 is an intake port 2 opening into a suction chamber of the side plate attached to the housing and a pressure port 3 connected to a pressure chamber of the side plate. Attached to the compressor housing 1 is a control disk 5 which separates the working chamber containing the impeller 4 of the compressor from the suction and pressure chamber of the side plate. The impeller lying axially in front of the control disk 5 is indicated in dashed lines in the drawing. The impeller 4 is offset with its axis of rotation 6 eccentrically with respect to the center axis of the compressor housing 1.

In der Steuerscheibe 5 ist eine radial unmittelbar an die Welle 8 des Laufrades 4 angrenzende, zur Nabe 9 des Laufrades 4 hin offene Verteilernut 10 ausgebildet. Die Verteilernut 10 erstreckt sich über den vollen Umfang der Laufradwelle 8. In die Verteilernut 10 mündet eine Zuführöffnung 11. Diese Zuführöffnung 11 steht, wie aus FIG 2 zu ersehen ist, mit einem mit Betriebsflüssigkeit angefüllten Raum 12 des Seitenschildes in Verbindung. Damit kann Betriebsflüssigkeit über die Zufuhröffnung 11 in die Verteilernut 10 einströmen. Von der Verteilernut 10 aus strömt die Betriebsflüssigkeit, wie durch Pfeile 13 angedeutet, durch den zwischen der Steuerscheibe 5 und der Laufradnabe 9 bestehenden Axialspalt 14 in den Arbeitsraum des Verdichters und vermengt sich mit der im Arbeitsraum den Flüssigkeitsring bildenden Betriebsflüssigkeit. Die den Axialspalt 14 durchströmende Betriebsflüssigkeit dichtet diesen Spalt ab.In the control disk 5 a radially adjacent to the shaft 8 of the impeller 4, to the hub 9 of the impeller 4 open distributor groove 10 is formed. The distributor groove 10 extends over the full circumference of the impeller shaft 8. A feed opening 11 opens into the distributor groove 10. This feed opening 11 is, as can be seen from FIG. 2, in connection with a space 12 of the side plate filled with operating fluid. Operating fluid can thus flow into the distributor groove 10 via the feed opening 11. From the distributor groove 10, the operating fluid flows, as indicated by arrows 13, through the axial gap 14 existing between the control disk 5 and the impeller hub 9 into the working space of the compressor and mixes with the operating fluid forming the liquid ring in the working space. The operating fluid flowing through the axial gap 14 seals this gap.

Bei dem Ausführungsbeispiel nach FIG 1 ist die Zuführöffnung 11 mit Bezug auf die durch einen Drehpfeil 15 gekennzeichnete Drehrichtung des Laufrades 4 in dem Bereich zwischen dem Ende des Saugschlitzes 16 und dem Beginn des Druckschlitzes 17 der Steuerscheibe 5 angeordnet. Auf der zum Saugschlitz 16 hin liegenden Seite der Zuführöffnung 11 ist ein als Finger 18 ausgebildetes, nach radial innen in die Verteilernut 10 ragendes Sperrglied vorgesehen. Der Finger 18 erstreckt sich radial bis zur Laufradwelle 8 und in axialer Richtung über die volle Tiefe der Verteilernut 10. Damit ist die Verteilernut auf der Seite zu dem Saugschlitz 16 hin praktisch vollständig verschlossen. Auf dieser Seite herrscht die größte Druckdifferenz zwischen der zugeführten Betriebsflüssigkeit und dem Druck in den am Saugschlitz vorbei rotierenden Laufradzellen. Wegen der vollständigen Abriegelung der Verteilernut 10 durch den Finger 18 kann die über die Zuführöffnung 11 in die Verteilernut 10 einströmende Betriebsflüssigkeit nicht direkt zu dem den Saugschlitz 16 benachbarten Bereich der Verteilernut strömen. Die Betriebsflüssigkeit muß vielmehr die Verteilernut in der durch Pfeile 19 angedeuteten Richtung durchströmen. Beim Durchströmen der Verteilernut 10 strömt ein Teil der Betriebsflüssigkeit auch nach radial außen durch den Axialspalt 14 und dichtet diesen ab.In the exemplary embodiment according to FIG. 1, the feed opening 11 is arranged in the region between the end of the suction slot 16 and the beginning of the pressure slot 17 of the control disk 5 with reference to the direction of rotation of the impeller 4 indicated by a rotating arrow 15. Provided on the side of the feed opening 11 facing the suction slot 16 is a locking member which is designed as a finger 18 and projects radially inward into the distributor groove 10. The finger 18 extends radially to the impeller shaft 8 and in the axial direction over the full depth of the distributor groove 10. The distributor groove on the side towards the suction slot 16 is thus practically completely closed. On this side there is the greatest pressure difference between the operating fluid supplied and the pressure in the impeller cells rotating past the suction slot. Because the distributor groove 10 is completely shut off by the finger 18, the operating liquid flowing into the distributor groove 10 via the feed opening 11 cannot flow directly to the region of the distributor groove adjacent to the suction slot 16. Rather, the operating fluid must flow through the distributor groove in the direction indicated by arrows 19. When flowing through the distributor groove 10, part of the operating fluid also flows radially outward through the axial gap 14 and seals it.

Da in den zu dem Druckschlitz 17 hin liegenden Bereich der Druckunterschied zwischen dem Zuführdruck der Betriebsflüssigkeit und dem in diesem Bereich in den Laufradzellen herrschenden Druck geringer ist, ist die in diesem Bereich über den Axialspalt 14 abströmende Flüssigkeitsmenge ebenfalls geringer, so daß für den weiteren Verlauf der Verteilernut noch eine genügende Flüssigkeitsmenge für eine ausreichende Abdichtung des Axialspaltes 14 zur Verfügung steht.Since the pressure difference between the supply pressure of the operating fluid and the pressure prevailing in the impeller cells in this area is smaller in the area lying towards the pressure slot 17, the amount of liquid flowing out in this area via the axial gap 14 is also smaller, so that for the further course the distributor groove still has a sufficient amount of liquid available for sufficient sealing of the axial gap 14.

Claims (4)

Flüssigkeitsringverdichter, mit einem im Verdichtergehäuse (1) gegenüber diesem exzentrisch gelagerten Laufrad (4) und mit mindestens einer auf der einen Stirnseite des Laufrades (4) angeordneten Steuerscheibe (5), welche für die Zu- und Abführung des zu verdichtenden Mediums mit einem Saug- und einem Druckschlitz (16 und 17) versehen ist und ferner in dem von der Nabe (9) des Laufrades (4) radial überdeckten Bereich eine umlaufende Verteilernut (10) aufweist, in welche über eine Zuführöffnung (11) Betriebsflüsssigkeit als Dichtflüssigkeit eingebracht ist,
dadurch gekennzeichnet,
daß im Bereich der Seite der Zuführöffnung (11), auf der der höhere Differenzdruck zwischen dem Zuführdruck der Betiebsflüssigkeit und dem Druck in den Laufradzellen herrscht ein radial in die Verteilernut (11) ragendes Sperrglied (18) vorgesehen ist.Liquid ring compressor, with one in the compressor housing (1) opposite to this eccentrically mounted impeller (4) and with at least one on one end of the impeller (4) arranged control disc (5), which for the supply and discharge of the medium to be compressed with a suction - And a pressure slot (16 and 17) is provided and also in the radially covered area of the hub (9) of the impeller (4) has a circumferential distributor groove (10) into which operating fluid is introduced as a sealing fluid via a feed opening (11) ,
characterized by
that in the region of the side of the feed opening (11) on which the higher differential pressure between the feed pressure of the operating fluid and the pressure in the impeller cells there is a locking member (18) projecting radially into the distributor groove (11). Flüssigkeitsringverdichter nach Anspruch 1,
dadurch gekennzeichnet,
daß sich das Sperrglied (18) über die volle radiale Höhe der Verteilernut (10) erstreckt.Liquid ring compressor according to claim 1,
characterized by
that the locking member (18) extends over the full radial height of the distributor groove (10). Flüssigkeitsringverdichter nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
daß die Verteilernut (10) radial unmittelbar an die Welle (8) des Laufrades (4) angrenzt.Liquid ring compressor according to claim 1 or 2,
characterized by
that the distributor groove (10) radially directly adjoins the shaft (8) of the impeller (4). Flüssigkeitsringverdichter nach Anspruch 1, 2 oder 3,
dadurch gekennzeichnet,
daß die Zuführöffnung (11) mit Bezug auf die Drehrichtung des Laufrades (4) in dem zwischen dem Ende des Saugschlitzes (16) und dem Beginn des Druckschlitzes (17) liegenden Bereich vorgesehen ist.Liquid ring compressor according to claim 1, 2 or 3,
characterized by
that the feed opening (11) with respect to the direction of rotation of the impeller (4) is provided in the region lying between the end of the suction slot (16) and the beginning of the pressure slot (17).
EP96112554A 1995-08-16 1996-08-02 Liquid ring compressor Expired - Lifetime EP0758717B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19530152 1995-08-16
DE19530152 1995-08-16

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Publication Number Publication Date
EP0758717A1 true EP0758717A1 (en) 1997-02-19
EP0758717B1 EP0758717B1 (en) 1998-11-04

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EP96112554A Expired - Lifetime EP0758717B1 (en) 1995-08-16 1996-08-02 Liquid ring compressor

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US (1) US5769609A (en)
EP (1) EP0758717B1 (en)
JP (1) JPH0953582A (en)
KR (1) KR970011417A (en)
CN (1) CN1079503C (en)
AT (1) ATE173058T1 (en)
AU (1) AU6207696A (en)
CA (1) CA2183309A1 (en)
DE (1) DE59600765D1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO316638B1 (en) * 2002-04-19 2004-03-15 Compressor Systems As Vaeskeringkompressor
US9175685B2 (en) 2008-12-18 2015-11-03 Gardner Denver Nash, Llc Liquid ring pump with gas scavenge device
TWI471487B (en) * 2012-09-14 2015-02-01 Tekomp Technology Co Ltd Screw Rotor Type Liquid Ring Compressor
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
CN112431758B (en) * 2020-11-27 2023-06-30 宁波益铸智能科技有限公司 Compressor auxiliary device for avoiding side wall collision by utilizing compression process

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR841223A (en) * 1938-04-28 1939-05-15 Sulzer Ag Pump with cell rotor sealed by a liquid ring
EP0090208A2 (en) * 1982-03-19 1983-10-05 Siemens Aktiengesellschaft Liquid ring compressor for gases

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB587585A (en) * 1944-07-19 1947-04-30 Nash Engineering Co A centrifugal pump or engine
DE1027358B (en) * 1955-02-08 1958-04-03 Siemens Ag Liquid ring pump
US3894812A (en) * 1974-02-19 1975-07-15 Atlantic Fluidics Inc Liquid ring vacuum pump-compressor
JPS555428A (en) * 1978-06-22 1980-01-16 Nakamura Suikan:Kk Water ring pump of side-air-port type
DE3124867C2 (en) * 1981-06-24 1983-11-17 Siemens AG, 1000 Berlin und 8000 München Liquid ring vacuum pump for gaseous media
US4422832A (en) * 1981-10-23 1983-12-27 The Nash Engineering Company Liquid ring pump with vanes in liquid ring
JPS6131686A (en) * 1984-07-23 1986-02-14 Fuji Electric Co Ltd Water sealing pump
JPS6243195U (en) * 1985-09-03 1987-03-16
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
DE3617344A1 (en) * 1986-05-23 1987-11-26 Siemens Ag METHOD FOR PRODUCING A CONTROL DISC OR A CONTROL SHIELD FOR A LIQUID RING MACHINE FOR MORE AGGRESSIVE MEDIA
JPH066951B2 (en) * 1988-12-22 1994-01-26 哲雄 森澤 Liquid ring vacuum pump

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR841223A (en) * 1938-04-28 1939-05-15 Sulzer Ag Pump with cell rotor sealed by a liquid ring
EP0090208A2 (en) * 1982-03-19 1983-10-05 Siemens Aktiengesellschaft Liquid ring compressor for gases

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Publication number Publication date
CN1079503C (en) 2002-02-20
DE59600765D1 (en) 1998-12-10
CA2183309A1 (en) 1997-02-17
US5769609A (en) 1998-06-23
CN1147596A (en) 1997-04-16
ATE173058T1 (en) 1998-11-15
KR970011417A (en) 1997-03-27
JPH0953582A (en) 1997-02-25
AU6207696A (en) 1997-02-20
EP0758717B1 (en) 1998-11-04

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