[go: up one dir, main page]

EP0758717B1 - Liquid ring compressor - Google Patents

Liquid ring compressor Download PDF

Info

Publication number
EP0758717B1
EP0758717B1 EP96112554A EP96112554A EP0758717B1 EP 0758717 B1 EP0758717 B1 EP 0758717B1 EP 96112554 A EP96112554 A EP 96112554A EP 96112554 A EP96112554 A EP 96112554A EP 0758717 B1 EP0758717 B1 EP 0758717B1
Authority
EP
European Patent Office
Prior art keywords
pressure
impeller
liquid
rotor
feed opening
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.)
Expired - Lifetime
Application number
EP96112554A
Other languages
German (de)
French (fr)
Other versions
EP0758717A1 (en
Inventor
Georg Dipl.-Ing. Plescher
Robert Dipl.-Ing. Siebenwurst
Bernhard Dipl.-Ing. Tews
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of EP0758717A1 publication Critical patent/EP0758717A1/en
Application granted granted Critical
Publication of EP0758717B1 publication Critical patent/EP0758717B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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 due to the DE-B-1027 358 known.
  • This compressor is in terms of the direction of rotation of the impeller directly after the pressure slot an opening is provided which is in flow with one in the Control disc trained radial transverse groove is connected.
  • the transverse groove in turn opens into an inner and an outer circumferential distributor groove.
  • operating fluid is in the transverse groove and through this into the distributor grooves. From there the operating fluid flows through the between the control disc and the impeller hub existing axial gap and seals this off. Results from the extent of the distributor groove increasing from the suction pressure to the compressor pressure Pressure history.
  • the invention has for its object a liquid ring compressor of the generic type so that the seal between the control disc and the impeller hub existing axial gap is significantly improved.
  • the task is solved by the in the license plate of claim 1 specified features.
  • Arrangement of a locking element in the distributor groove becomes one from the feed opening to the area of the larger one Pressure difference directed stronger outflow of the Operating fluid sealing axial gap prevented.
  • the Operating fluid is through the arrangement of the locking member much more on the corresponding side of the feed opening directed to the area where the pressure difference between supply pressure the operating fluid and the pressure in the Impeller cells is less large. This results in the full extent of the distributor groove an overall better distribution the operating fluid sealing the axial gap.
  • the feed opening in relation on the direction of rotation of the impeller in the between the end of the suction slot and the beginning of the pressure slot Area is provided.
  • the flow direction is correct of the operating fluid in the distributor groove with the Direction of rotation of the impeller coincide, so that the operating fluid in the distributor groove by the rotating impeller is still carried in the circumferential direction.
  • With 1 is the compressor housing of a liquid ring compressor designated. On the housing 1 is in a suction space of the side plate attached to the housing Intake 2 and one with a pressure chamber of the side plate connected pressure port 3 provided. To the compressor housing 1 is a the impeller 4 of the compressor containing working space from the suction and pressure space of the Control plate 5 separating side plate attached. The axial impeller lying in front of the control disk 5 is in the drawing indicated by dashed lines. The impeller 4 is with his Axis of rotation 6 eccentrically with respect to the center axis of the compressor housing 1 offset.
  • control disc 5 is a radially directly to the Shaft 8 of the impeller 4 adjacent to the hub 9 of the impeller 4 open distributor groove 10 formed.
  • the distributor groove 10 extends over the entire circumference of the impeller shaft 8.
  • This Feed opening 11 is, as can be seen from FIG. 2, with a space 12 of the side plate filled with operating fluid in connection. So that operating fluid can over the supply opening 11 flow into the distributor groove 10.
  • From the distributor groove 10 flows out of the operating fluid, such as indicated by arrows 13, by the between the control disc 5 and the impeller hub 9 existing axial gap 14 in the working space of the compressor and mixes with that in the Working space the operating fluid forming the liquid ring.
  • the operating fluid flowing through the axial gap 14 seals this gap.
  • the feed opening is 11 with reference to that indicated by a rotating arrow 15
  • Towards the suction slot 16 lying side of the feed opening 11 is a finger 18 formed, radially inward into the distributor groove 10 projecting locking member provided.
  • the finger 18 extends radially up to the impeller shaft 8 and in the axial direction the full depth of the distributor groove 10. This is the Manifold groove on the side towards the suction slot 16 practically completely closed. On this side there is the greatest pressure difference between the supplied Operating fluid and the pressure in the at the suction slot passing rotating impeller cells.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Flanged Joints, Insulating Joints, And Other Joints (AREA)
  • Separating Particles In Gases By Inertia (AREA)
  • Compressor (AREA)

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 due to the DE-B-1027 358 known. This compressor is in terms of the direction of rotation of the impeller directly after the pressure slot an opening is provided which is in flow with one in the Control disc trained radial transverse groove is connected. The transverse groove in turn opens into an inner and an outer circumferential distributor groove. Through the opening, which is due their spatial location from the liquid ring of the compressor is covered, operating fluid is in the transverse groove and through this into the distributor grooves. From there the operating fluid flows through the between the control disc and the impeller hub existing axial gap and seals this off. Results from the extent of the distributor groove increasing from the suction pressure to the compressor pressure Pressure history. So the pressure difference between that Supply pressure of the operating fluid and the pressure in the individual Impeller cells are not constant. This leads to the fact that in Areas of a higher pressure differential therefore more Operating fluid is pressed through the axial gap as 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 a liquid ring compressor of the generic type so that the seal between the control disc and the impeller hub existing axial gap 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 insgesamt bessere Verteilung der den Axialspalt abdichtenden Betriebsflüssigkeit.The task is solved by the in the license plate of claim 1 specified features. By the described Arrangement of a locking element in the distributor groove becomes one from the feed opening to the area of the larger one Pressure difference directed stronger outflow of the Operating fluid sealing axial gap prevented. The Operating fluid is through the arrangement of the locking member much more on the corresponding side of the feed opening directed to the area where the pressure difference between supply pressure the operating fluid and the pressure in the Impeller cells is less large. This results in the full extent of the distributor groove an overall better distribution the operating fluid sealing the axial gap.

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

Dadurch, daß die Verteilernut radial unmittelbar an die Welle des Laufrades angrenzt, ergibt sich eine maximale radiale Länge der Abdichtstrecke.The fact that the distributor groove radially directly to the shaft adjacent to 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 in relation on the direction of rotation of the impeller in the between the end of the suction slot and the beginning of the pressure slot Area is provided. In this case the flow direction is correct of the operating fluid in the distributor groove with the Direction of rotation of the impeller coincide, so that the operating fluid in the distributor groove by the rotating impeller is still carried in the circumferential direction.

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.With 1 is the compressor housing of a liquid ring compressor designated. On the housing 1 is in a suction space of the side plate attached to the housing Intake 2 and one with a pressure chamber of the side plate connected pressure port 3 provided. To the compressor housing 1 is a the impeller 4 of the compressor containing working space from the suction and pressure space of the Control plate 5 separating side plate attached. The axial impeller lying in front of the control disk 5 is in the drawing indicated by dashed lines. The impeller 4 is with his Axis of rotation 6 eccentrically with respect to the center axis of the compressor housing 1 offset.

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 disc 5 is a radially directly to the Shaft 8 of the impeller 4 adjacent to the hub 9 of the impeller 4 open distributor groove 10 formed. The distributor groove 10 extends over the entire circumference of the impeller shaft 8. In the distributor groove 10 opens a feed opening 11. This Feed opening 11 is, as can be seen from FIG. 2, with a space 12 of the side plate filled with operating fluid in connection. So that operating fluid can over the supply opening 11 flow into the distributor groove 10. From the distributor groove 10 flows out of the operating fluid, such as indicated by arrows 13, by the between the control disc 5 and the impeller hub 9 existing axial gap 14 in the working space of the compressor and mixes with that in the Working space the operating fluid forming the liquid ring. 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 is 11 with reference to that indicated by a rotating arrow 15 Direction of rotation of the impeller 4 in the area between the end of the suction slot 16 and the beginning of the pressure slot 17 of the Control disc 5 arranged. Towards the suction slot 16 lying side of the feed opening 11 is a finger 18 formed, radially inward into the distributor groove 10 projecting locking member provided. The finger 18 extends radially up to the impeller shaft 8 and in the axial direction the full depth of the distributor groove 10. This is the Manifold groove on the side towards the suction slot 16 practically completely closed. On this side there is the greatest pressure difference between the supplied Operating fluid and the pressure in the at the suction slot passing rotating impeller cells. Because of the full Locking the distributor groove 10 by the finger 18 can flowing into the distributor groove 10 via the feed opening 11 Operating fluid not directly to the suction slot 16 flow adjacent area of the distributor groove. The Rather, the operating fluid must be in the distributor groove flow through by arrows 19 indicated direction. At the Part of the flows through the distributor groove 10 Operating fluid also radially outwards 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 in the area towards the printing slot 17 Pressure difference between the supply pressure of the operating fluid and that in this area in the impeller cells prevailing pressure is lower, is that in this area Quantity of liquid flowing out via the axial gap 14 likewise less so that for the further course of the distributor groove still a sufficient amount of liquid for one sufficient sealing of the axial gap 14 is available stands.

Claims (4)

  1. Liquid-ring compressor having a rotor (4) mounted in the compressor casing (1) eccentrically relative to the latter and having at least one control disc (5) which is arranged on the one end face of the rotor (4), is provided with a suction and a pressure slot (16 and 17) for the feed and discharge of the medium to be compressed and furthermore has an encircling distribution groove (10) in the area covered radially by the hub (9) of the rotor (4), into which distribution groove (10) operating liquid is introduced as sealing liquid via a feed opening (11), characterized in that a blocking element (18) projecting radially into the distribution groove (10) is provided in the area of the side of the feed opening (11) on which the greater pressure difference between the feed pressure of the operating liquid and the pressure in the rotor cells prevails.
  2. Liquid-ring compressor according to Claim 1, characterized in that the blocking element (18) extends over the full radial height of the distribution groove (10).
  3. Liquid-ring compressor according to Claim 1 or 2, characterized in that the distribution groove (10) directly adjoins the shaft (8) of the rotor (4) in the radial direction.
  4. Liquid-ring compressor according to Claims 1, 2 or 3, characterized in that the feed opening (11), in relation to the direction of rotation of the rotor (4), is provided in the area lying between the end of the suction slot (16) and the start 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

Publications (2)

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

Family

ID=7769637

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96112554A Expired - Lifetime EP0758717B1 (en) 1995-08-16 1996-08-02 Liquid ring compressor

Country Status (9)

Country Link
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
KR101581490B1 (en) * 2008-12-18 2015-12-30 가드너 덴버 내쉬 엘엘씨 Channel formed in a liquid ring pump and a cylinder of the same
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

Family Cites Families (15)

* 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
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
DE3210161C1 (en) * 1982-03-19 1983-10-06 Siemens Ag Liquid ring compressor for gases
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

Also Published As

Publication number Publication date
DE59600765D1 (en) 1998-12-10
AU6207696A (en) 1997-02-20
CA2183309A1 (en) 1997-02-17
KR970011417A (en) 1997-03-27
ATE173058T1 (en) 1998-11-15
US5769609A (en) 1998-06-23
CN1079503C (en) 2002-02-20
EP0758717A1 (en) 1997-02-19
CN1147596A (en) 1997-04-16
JPH0953582A (en) 1997-02-25

Similar Documents

Publication Publication Date Title
DE3308227C2 (en)
DE69313560T2 (en) Hydraulic vane pump with improved axial pressure compensation and pressure flow properties
DE3223703A1 (en) FLUID-LOCKED SHAFT SEAL WITH FLUID SUPPLY AND EXHAUST HOLES
DE4020520A1 (en) AGGREGATE FOR PROCESSING FUEL FROM THE STORAGE TANK TO THE INTERNAL COMBUSTION ENGINE OF A MOTOR VEHICLE
DE3839689C2 (en) Hydraulic pump unit that can be assembled as a modular system and driven by an electric motor
DE4428633A1 (en) Fuel pump for supplying fuel to a vehicle engine
DE4318122A1 (en) Unit for delivering fuel from a fuel tank to the internal combustion engine of a motor vehicle
EP0645521A1 (en) Liquid ring gas pump
EP0758717B1 (en) Liquid ring compressor
DE2825616A1 (en) GEAR PUMP
DE3440850C2 (en)
EP0680562B1 (en) Liquid ring machine
EP0245626B1 (en) Liquid-ring machine
DE69203687T2 (en) Hydraulic rotary wing machine.
DE69011731T2 (en) Pump.
DE4221184A1 (en) Fuel delivery pump for vehicle IC engine - uses space between impeller and delivery channel to control direction of flow
DE3444392C2 (en)
EP1518055B1 (en) Liquid ring pump
DE19758340A1 (en) Multi-flow liquid ring pump
DE1553050C3 (en) Rotary piston machine with a ring cylinder
EP0476450B1 (en) Axial piston pump, particularly for water high-pressure cleaner
DE19825521C2 (en) Liquid ring pump
DE69416895T2 (en) Pump impeller
DE2907076A1 (en) Precessing eccentric gear motor - has rotary valve with circumferential annular and inclined grooves for connecting displacement chambers
DE2650843C2 (en) Discharge pump for liquids under vacuum

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB IT LI NL SE

17P Request for examination filed

Effective date: 19970317

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 19971210

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FI FR GB IT LI NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19981104

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19981104

Ref country code: FI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19981104

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19981104

REF Corresponds to:

Ref document number: 173058

Country of ref document: AT

Date of ref document: 19981115

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 59600765

Country of ref document: DE

Date of ref document: 19981210

ET Fr: translation filed
ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19990112

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19990204

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990802

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990831

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
BERE Be: lapsed

Owner name: SIEMENS A.G.

Effective date: 19990831

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000810

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000831

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010802

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20010802

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20050819

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20050930

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20060831

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070301

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20070430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070802