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EP2587065B1 - Liquid ring compressor - Google Patents

Liquid ring compressor Download PDF

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Publication number
EP2587065B1
EP2587065B1 EP20110186724 EP11186724A EP2587065B1 EP 2587065 B1 EP2587065 B1 EP 2587065B1 EP 20110186724 EP20110186724 EP 20110186724 EP 11186724 A EP11186724 A EP 11186724A EP 2587065 B1 EP2587065 B1 EP 2587065B1
Authority
EP
European Patent Office
Prior art keywords
part section
curvature
rotation
liquid ring
point
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.)
Active
Application number
EP20110186724
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German (de)
French (fr)
Other versions
EP2587065A1 (en
Inventor
Peter Bucher
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.)
Pompetravaini Nsb AG
Original Assignee
NSB Gas Processing AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSB Gas Processing AG filed Critical NSB Gas Processing AG
Priority to EP20110186724 priority Critical patent/EP2587065B1/en
Priority to PCT/EP2012/071101 priority patent/WO2013060754A2/en
Publication of EP2587065A1 publication Critical patent/EP2587065A1/en
Application granted granted Critical
Publication of EP2587065B1 publication Critical patent/EP2587065B1/en
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C2250/00—Geometry
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the invention relates to a liquid ring compressor according to the preamble of claim 1.
  • the publication EP 0 565 232 B1 discloses in Figure 11 a two-stage liquid ring compressor, wherein the two stages are arranged one after the other in the direction of rotation, so that the liquid ring compressor has two circumferentially spaced compression zones.
  • the liquid ring compressor has an elliptically extending housing, within which the rotor of the pump is arranged. This liquid ring compressor has the disadvantage that its efficiency is not optimal.
  • the object of the invention is to form an economically advantageous liquid ring compressor, which in particular has an improved efficiency.
  • a liquid ring compressor comprising a ring housing and a paddle wheel, wherein the paddle wheel is arranged within the ring housing and is rotatably mounted about a rotation axis and in a rotational direction, wherein the paddle wheel has a plurality of spaced apart in the direction of rotation blades, and wherein the ring housing has a circumferentially extending housing inner wall oriented toward the paddle wheel, the housing inner wall having a first section and a third section which are curved with respect to the axis of rotation, preferably circular and with an eccentricity radius of curvature, and which are mutually symmetrical with respect to the axis of rotation are arranged extending, and wherein the housing inner wall has a second portion which connects the first portion to the third portion, and wherein the second portion between the first subsection and the third subsection has an eccentricity point which has a maximum distance in a direction radial to the axis of rotation with respect to a circular path defined by the outer edges of the blades, and where
  • the profile of the housing inner wall of the inventive liquid ring compressor has the advantage that the ejection in the region of the outlet opening takes place more advantageously.
  • the volume of the liquid ring compressor in the region of the outlet opening in the direction of rotation is increasingly reduced, with the result that the liquid to be pumped by the liquid ring compressor experiences an increase in pressure in the region of the outlet opening, so that the fluid to be pumped at a higher pressure toward the outlet opening is encouraged.
  • the housing inner wall of the inventive liquid ring compressor is designed such that the suction of the liquid ring compressor in the inlet opening in the direction of rotation additionally increases, with the result that the liquid ring compressor has a larger intake volume, so that a larger amount of fluid to be pumped enters the intake volume via the inlet opening.
  • the inventive liquid ring compressor could also be called or used as a liquid ring pump, liquid ring vacuum pump or liquid ring compressor or liquid ring vacuum compressor.
  • Fig. 1 shows a section through a liquid ring compressor according to the invention 1.
  • the liquid ring compressor 1 comprises a liquid ring compressor housing 2 with an interior 2a, wherein in the interior 2a a rotatable impeller 4 is arranged, wherein the impeller 4 has a plurality of circumferentially spaced apart blades 4a, and wherein the impeller 4 is rotatably mounted about a center of rotation 4b.
  • a fixed inlet and outlet device 6 is arranged, which has two circumferentially extending inlet openings 7 and two circumferentially extending outlet openings 8.
  • the inlet and outlet device 6 is also referred to as internal distributor.
  • the liquid ring compressor 1 is configured in the illustrated embodiment as a double-flow pump by having these two inlet openings 7, two outlet openings 8 and also two mutual compression spaces 10a.
  • the interior 2a is bounded in the circumferential direction by a housing inner wall 3, which surrounds the impeller 4 in the circumferential direction from the outside, wherein the housing inner wall 3 is aligned to the impeller 4 out.
  • the housing inner wall 3 comprises a plurality of subsections 3a - 3n, which together form the in Form the circumferential direction of the housing inner wall 3.
  • In the interior 2a is a liquid which is conveyed by the impeller 4 in the direction of rotation 5, and which forms a liquid ring 9 with a boundary line 9a.
  • the space between the boundary line 9a and the inlet and outlet device 6 forms a delivery chamber 10, within which a gas is pumped from the inlet opening 7 to the outlet opening 8.
  • the delivery space 10 is divided in the circumferential direction into a plurality of sub-conveying spaces 10a which are successively delimited by a respective bucket 4a, wherein the volume of the sub-conveying spaces 10a increases in the area of the inlet opening 7 in the direction 9b and thereby performs a suction movement, and wherein reduces the volume of the sub-conveying spaces 10a toward the outlet opening 8 in the direction 9c, whereby a compression movement is carried out.
  • This pumping process takes place both in the FIG. 1
  • the housing inner wall 3 has a first section 3d and a third section 3f, which run concentric to the center of rotation 4b of the impeller 4 and the center of rotation 4b a distance R or a radius of excision R e , also referred to as Exzentrizticianskrümmungsradius R e .
  • a second subsection 3e extends between the first subsection 3d and the third subsection 3f.
  • a fourth subsection 3g extends between the third subsection 3f and the first subsection 3d.
  • the housing inner wall 3 has at the transitions of the sections 3d, 3e, 3f, 3g each have a kink K1, K2, K3, K4 on. These can be edged, angular or rounded.
  • the liquid ring compressor 1 has a first center 11a and a second center 11b, which are spaced by the same length with respect to the center of rotation 4b of the impeller 4.
  • the dashed line 11c shows a circle with first center 11a and eccentricity radius R e .
  • the dashed line 11d shows a circle with the second center 11b and the eccentricity radius R e .
  • the housing inner wall 3 also has two opposite eccentricity points 3h, at which the housing inner wall 3 has the greatest distance with respect to the center of rotation 4b.
  • the housing inner wall 3 runs along the second part section 3e such that the second part section 3e has no kinks, and that the second part section 3e has sections with different radii of curvature.
  • This configuration of the course of the housing inner wall 3 has the consequence that the suction movement 9b of the boundary line 9a is increased or increased, and that the compression movement 9c of the boundary line 9a is increased or amplified, resulting in an increase in the pumping capacity of the liquid ring compressor 1 result.
  • the radii Ri, Rk, Rl, Rm can vary in the circumferential direction. In a further advantageous embodiment, however, each of the radii Ri, Rk, Rl, Rm may also have a constant value.
  • FIG. 2 shows in a section perpendicular to the axis of rotation 4b, a further embodiment of a liquid ring compressor 1 with housing 2 and housing inner wall 3, wherein the liquid ring pump 1 is out of operation and therefore in the interior of the liquid ring compressor 1 no fluid.
  • the liquid ring compressor 1 has, as ready in FIG. 1 described, a housing inner wall 3 with circumferentially successively arranged first, second, third and fourth section 3d, 3e, 3f, 3g and arranged therebetween kinks or transition areas K1, K2, K3, K4.
  • all four radii Ri, Rk, Rl, Rm in the subsection 3e have a constant value.
  • the two radii Rm and Ri are larger than the eccentricity radius R e , whereas the two radii Rk and Rl are smaller than the eccentricity radius R e .
  • the portion 3e no kinks, which means that the sections with radii Rl, Rm, Ri, Rk at their transition points u 1, 3h and u4 in the direction of rotation 5 are mutually tangential, so that these transition points u 1, 3h and u4 have no kink or discontinuity.
  • FIG. 3 shows a detail view of the left upper part of in FIG. 2
  • the second section 3e comprises the following four sections successively in the direction of rotation 5, a seventh section 31 with radius of curvature R1, an eighth section 3m with radius of curvature Rm, which follows the junction u4, a fifth section 3i with radius of curvature Ri, which follows after the eccentricity point 3h, and a sixth Subsection 3k with radius of curvature Rk, which follows after the transition point u 1.
  • the second section 3e is mirror-symmetrical with respect to an axis passing through the points 3h and 4b.
  • the circular path K represents the circle described by the outer edge (4c) of the blades 4a of the blade wheel 4.
  • the distance A between the circular path K and the housing inner wall 3 increases from the region of the opening point 7a of the inlet opening 7 in the direction of rotation 5, and points in Eccentricity point 3h the highest value A1.
  • the distance A then reduces to the region of the closing point 8b of the outlet opening eighth FIG. 3 also shows the circular line 11c, which is defined by a circle with eccentricity radius R e and the first center 11a.
  • the housing inner wall 3 now runs along the fifth and sixth subsection 3i, 3k in such a way that the radius of curvature Ri has a greater value than the eccentricity radius R e , so that the fifth subsection 3i moves further away from the circular line 11c, and that the radius of curvature Rk is smaller Has value as the eccentricity radius R e , so that the sixth portion 3k of the circular line 11c approaches again.
  • the sixth section 3k is in an advantageous embodiment as in FIG. 3 represented along the outlet opening 8 arranged to effect through the course of the housing inner wall 3 along the sixth section 3k an increased compression movement 9c on the liquid ring 9 or on its boundary line 9a, thereby increasing the conveying effect to the outlet port 8 out.
  • FIG. 4 shows a further embodiment of a course of the housing inner wall 3.
  • the left half of the second section 3e is shown, which is a fifth Part 3i and a sixth section 3k includes.
  • the fifth section 3i has a radius of curvature Ri with a center of rotation zi.
  • the sixth section 3k has a radius of curvature Rk with a center of rotation zk.
  • the radii Ri, Rk and the centers of rotation zi, zk are dimensioned and arranged such that the tangents of the fifth and sixth part sections 3i, 3k are identical at the transition point u 1, so that the transition point u1 has no kink or discontinuity.
  • the radii of curvature Ri, Rk could also have varying values in the direction of rotation 5, preferably such that the radii Ri are greater than R and that the radii Rk are smaller than R, and preferably such that the tangents of the fifth and sixth part sections 3i, 3k are identical at the transition point u 1.
  • FIG. 5 shows a partial view of a section through the in FIG. 1 shown liquid ring compressor 1 along the section line BB. From this, the course of the blade wheel 4 with blade 4a within the housing 2 can be seen.

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

Description

Die Erfindung betrifft einen Flüssigkeitsringverdichter gemäss dem Oberbegriff von Anspruch 1.The invention relates to a liquid ring compressor according to the preamble of claim 1.

Stand der TechnikState of the art

Die Druckschrift EP 0 565 232 B1 offenbart in Figur 11 einen zweistufigen Flüssigkeitsringverdichter, wobei die beiden Stufen in Drehrichtung nacheinander angeordnet sind, sodass der Flüssigkeitsringverdichter zwei in Umfangsrichtung beabstandet angeordnete Kompressionszonen aufweist. Der Flüssigkeitsringverdichter weist ein elliptisch verlaufendes Gehäuse auf, innerhalb welchem der Rotor der Pumpe angeordnet ist. Dieser Flüssigkeitsringverdichter weist den Nachteil auf, dass deren Wirkungsgrad nicht optimal ist.The publication EP 0 565 232 B1 discloses in Figure 11 a two-stage liquid ring compressor, wherein the two stages are arranged one after the other in the direction of rotation, so that the liquid ring compressor has two circumferentially spaced compression zones. The liquid ring compressor has an elliptically extending housing, within which the rotor of the pump is arranged. This liquid ring compressor has the disadvantage that its efficiency is not optimal.

Die Druckschrift DE 1021976 , die als nächstliegenden Stand der Technik angesehen wird, offenbart einen zweistufigen Flüssigkeitsringverdichter dessen Gehäuseinnenhand aus Teilabschnitte besteht.The publication DE 1021976 , which is considered as the closest prior art, discloses a two-stage liquid ring compressor whose housing inner hand consists of sections.

Darstellung der ErfindungPresentation of the invention

Aufgabe der Erfindung ist es einen wirtschaftlich vorteilhafteren Flüssigkeitsringverdichter zu bilden, welche insbesondere einen verbesserten Wirkungsgrad aufweist.The object of the invention is to form an economically advantageous liquid ring compressor, which in particular has an improved efficiency.

Diese Aufgabe wird gelöst mit einem Flüssigkeitsringverdichter aufweisend die Merkmale von Anspruch 1. Die Unteransprüche 2 bis 10 betreffen weitere, vorteilhafte Ausgestaltungen.This object is achieved with a liquid ring compressor having the features of claim 1. The dependent claims 2 to 10 relate to further advantageous embodiments.

Die Aufgabe wird insbesondere gelöst mit einem Flüssigkeitsringverdichter umfassend ein Ringgehäuse sowie ein Schaufelrad, wobei das Schaufelrad innerhalb des Ringgehäuses angeordnet ist und um eine Drehachse und in eine Drehrichtung drehbar gelagert ist, wobei das Schaufelrad eine Mehrzahl von in Drehrichtung gegenseitig beabstandet angeordnete Schaufeln aufweist, und wobei das Ringgehäuse eine zum Schaufelrad hin ausgerichtete, in Umfangsrichtung verlaufende Gehäuseinnenwand aufweist, wobei die Gehäuseinnenwand einen ersten Teilabschnitt und einen dritten Teilabschnitt aufweist, die bezüglich der Drehachse gekrümmt, vorzugsweise kreisförmig und mit einem Exzentrizitätskrümmungsradius verlaufen, und die bezüglich der Drehachse gegenüberliegend und gegenseitig symmetrisch verlaufend angeordnet sind, und wobei die Gehäuseinnenwand einen zweiten Teilabschnitt aufweist, der den ersten Teilabschnitt mit dem dritten Teilabschnitt verbindet, und wobei der zweite Teilabschnitt zwischen dem ersten Teilabschnitt und dem dritten Teilabschnitt einen Exzentrizitätspunkt aufweist, welcher in zur Drehachse radialen Richtung bezüglich einer durch die Aussenkanten der Schaufeln definierten Kreisbahn einen maximalen Abstand aufweist, und wobei der zweite Teilabschnitt zwischen dem Exzentrizitätspunkt und dem dritten Teilabschnitt in Drehrichtung aus einem fünften und einem sechsten Teilabschnitt besteht, wobei der fünfte Teilabschnitt einen gekrümmten Verlauf aufweist mit Krümmungsradien die grösser sind als der Exzentrizitätskrümmungsradius des ersten Teilabschnittes, und wobei der sechste Teilabschnitt einen gekrümmten Verlauf aufweist mit Krümmungsradien die kleiner sind als der Exzentrizitätskrümmungsradius des ersten Teilabschnittes, und wobei der fünfte und sechste Teilabschnitt an deren Übergangsstelle gegenseitig tangential verlaufen, und wobei innerhalb des Ringgehäuses eine Ein- und Auslassvorrichtung angeordnet ist, welche eine Auslassöffnung aufweist, wobei sich die Auslassöffnung innerhalb des Bereichs zwischen dem Exzentrizitätspunkt und dem dritten Teilabschnitt in Drehrichtung streckt. Die sich in Drehrichtung erstreckende Auslassöffnung erstreckt sich vorzugsweise entlang eines Teilabschnittes des Bereichs zwischen dem Exzentrizitätspunkt und dem dritten Teilabschnitt.The object is achieved in particular with a liquid ring compressor comprising a ring housing and a paddle wheel, wherein the paddle wheel is arranged within the ring housing and is rotatably mounted about a rotation axis and in a rotational direction, wherein the paddle wheel has a plurality of spaced apart in the direction of rotation blades, and wherein the ring housing has a circumferentially extending housing inner wall oriented toward the paddle wheel, the housing inner wall having a first section and a third section which are curved with respect to the axis of rotation, preferably circular and with an eccentricity radius of curvature, and which are mutually symmetrical with respect to the axis of rotation are arranged extending, and wherein the housing inner wall has a second portion which connects the first portion to the third portion, and wherein the second portion between the first subsection and the third subsection has an eccentricity point which has a maximum distance in a direction radial to the axis of rotation with respect to a circular path defined by the outer edges of the blades, and wherein the second subsection between the eccentricity point and the third subsection in the direction of rotation consists of a fifth and a sixth subsection, the fifth subsection having a curved course having radii of curvature greater than the eccentricity curvature radius of the first subsection, and wherein the sixth subsection has a curved course with radii of curvature smaller than the radius of curvature of the eccentricity of the first section, and with the fifth and sixth sections mutually tangent at their transition point, and inside the ring housing an inlet and outlet device having an outlet opening, the outlet opening being within the outlet opening Range between the Exzentrizitätspunkt and the third section in the direction of rotation stretches. The rotationally extending outlet opening preferably extends along a partial section of the region between the point of eccentricity and the third partial section.

Der Verlauf der Gehäuseinnenwand des erfindungsgemässen Flüssigkeitsringverdichters weist den Vorteil auf, dass das Ausstossen im Bereich der Auslassöffnung vorteilhafter erfolgt. In einer vorteilhaften Ausgestaltung wird das Volumen des Flüssigkeitsringverdichters im Bereich der Auslassöffnung in Drehrichtung zunehmend verkleinert, was zur Folge hat, das das vom Flüssigkeitsringverdichter zu pumpende Fluid im Bereich der Auslassöffnung eine Druckerhöhung erfährt, sodass das zu pumpende Fluid mit einem höheren Druck zur Auslassöffnung hin gefördert wird.The profile of the housing inner wall of the inventive liquid ring compressor has the advantage that the ejection in the region of the outlet opening takes place more advantageously. In an advantageous embodiment, the volume of the liquid ring compressor in the region of the outlet opening in the direction of rotation is increasingly reduced, with the result that the liquid to be pumped by the liquid ring compressor experiences an increase in pressure in the region of the outlet opening, so that the fluid to be pumped at a higher pressure toward the outlet opening is encouraged.

In einer weiteren vorteilhaften Ausführungsform ist die Gehäuseinnenwand des erfindungsgemässen Flüssigkeitsringverdichters derart ausgestaltet, dass sich der Ansaugraum des Flüssigkeitsringverdichters im Bereich der Einlassöffnung in Drehrichtung zusätzlich vergrössert, was zur Folge hat, dass der Flüssigkeitsringverdichter ein grösseres Ansaugvolumen aufweist, sodass eine grössere Menge des zu pumpenden Fluids über die Einlassöffnung in das Ansaugvolumen gelangt.In a further advantageous embodiment, the housing inner wall of the inventive liquid ring compressor is designed such that the suction of the liquid ring compressor in the inlet opening in the direction of rotation additionally increases, with the result that the liquid ring compressor has a larger intake volume, so that a larger amount of fluid to be pumped enters the intake volume via the inlet opening.

Der erfindungsgemässe Flüssigkeitsringverdichter könnte auch als Flüssigkeitsringpumpe, Flüssigkeitsringvakuumpumpe oder Flüssigkeitsringkompressor oder Flüssigkeitsringvakuumkompressor bezeichnet bzw. eingesetzt werden.The inventive liquid ring compressor could also be called or used as a liquid ring pump, liquid ring vacuum pump or liquid ring compressor or liquid ring vacuum compressor.

Die Erfindung wird nachfolgend an Hand von Ausführungsbeispielen im Detail erläutert.The invention will be explained below with reference to exemplary embodiments in detail.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die zur Erläuterung der Ausführungsbeispiele verwendeten Zeichnungen zeigen:

Fig. 1
einen senkrecht zur Achse des Schaufelrades verlaufenden Schnitt durch einen Flüssigkeitsringverdichter umfassend ein Gehäuse sowie einen Rotor;
Fig. 2
einen Schnitt durch ein weiteres Ausführungsbeispiel eines Flüssigkeitsringverdichters;
Fig. 3
eine Detailansicht des linken Teils der in Figur 2 dargestellten Flüssigkeitsringverdichters;
Fig. 4
eine Detailansicht eines weiteren Ausführungsbeispiel eines Flüssigkeitsringverdichters;
Fig. 5
einen Schnitt durch Figur 1 entlang der Schnittlinie B-B.
The drawings used to explain the embodiments show:
Fig. 1
a section perpendicular to the axis of the impeller through a liquid ring compressor comprising a housing and a rotor;
Fig. 2
a section through another embodiment of a liquid ring compressor;
Fig. 3
a detail view of the left part of the in FIG. 2 illustrated liquid ring compressor;
Fig. 4
a detailed view of another embodiment of a liquid ring compressor;
Fig. 5
a cut through FIG. 1 along the section line BB.

Grundsätzlich sind in den Zeichnungen gleiche Teile mit gleichen Bezugszeichen versehen.Basically, the same parts are given the same reference numerals in the drawings.

Wege zur Ausführung der ErfindungWays to carry out the invention

Fig. 1 zeigt einen Schnitt durch einen erfindungsgemässen Flüssigkeitsringverdichter 1. Der Flüssigkeitsringverdichter 1 umfasst ein Flüssigkeitsringverdichtergehäuse 2 mit einem Innenraum 2a, wobei im Innenraum 2a ein drehbares Schaufelrad 4 angeordnet ist, wobei das Schaufelrad 4 eine Vielzahl von in Umfangsrichtung gegenseitig beabstandet angeordnete Schaufeln 4a aufweist, und wobei das Schaufelrad 4 um ein Drehzentrum 4b drehbar gelagert ist. In Zentrum des Flüssigkeitsringverdichters 1 ist eine fest stehende Ein- und Auslassvorrichtung 6 angeordnet, welche zwei in Umfangsrichtung verlaufende Einlassöffnungen 7 und zwei in Umfangsrichtung verlaufende Auslassöffnungen 8 aufweist. Die Ein- und Auslassvorrichtung 6 wird auch als innerer Verteiler bezeichnet. Der Flüssigkeitsringverdichter 1 ist im dargestellten Ausführungsbeispiel als zweiflutige Pumpe ausgestaltet, indem diese zwei Einlassöffnungen 7, zwei Auslassöffnungen 8 und zudem zwei gegenseitige Kompressionsräume 10a aufweist. Der Innenraum 2a ist in Umfangsrichtung durch eine Gehäuseinnenwand 3 begrenzt, welche das Schaufelrad 4 in Umfangsrichtung von Aussen umschliesst, wobei die Gehäuseinnenwand 3 zum Schaufelrad 4 hin ausgerichtet ist. Die Gehäuseinnenwand 3 umfasst eine Mehrzahl von Teilabschnitten 3a - 3n, welche gemeinsam die in Umfangsrichtung verlaufende Gehäuseinnenwand 3 ausbilden. Im Innenraum 2a befindet sich eine Flüssigkeit, welche vom Schaufelrad 4 in Drehrichtung 5 gefördert wird, und welche einen Flüssigkeitsring 9 mit einer Grenzlinie 9a ausbildet. Der Raum zwischen der Grenzlinie 9a und der Ein- und Auslassvorrichtung 6 bildet einen Förderraum 10, innerhalb welchem ein Gas von der Einlassöffnung 7 zur Auslassöffnung 8 gepumpt wird. Wie in Figur 1 dargestellt, ist der Förderraum 10 in Umfangsrichtung in eine Mehrzahl nacheinander folgende und durch jeweils eine Schaufel 4a gegenseitig begrenzte Teilförderräume 10a aufgeteilt, wobei sich das Volumen der Teilförderräume 10a im Bereich der Einlassöffnung 7 in Richtung 9b vergrössert und dadurch eine Saugbewegung ausführt, und wobei sich das Volumen der Teilförderräume 10a zur Auslassöffnung 8 hin in Richtung 9c verkleinert, wodurch eine Kompressionsbewegung ausgeführt wird. Dieser Pumpvorgang findet sowohl in dem in Figur 1 links oben dargestellten Förderraum 10 beziehungsweise den Teilförderräumen 10a als auch in dem rechts unten dargestellten Förderraum 10 beziehungsweise den Teilförderräumen 10a statt. Fig. 1 shows a section through a liquid ring compressor according to the invention 1. The liquid ring compressor 1 comprises a liquid ring compressor housing 2 with an interior 2a, wherein in the interior 2a a rotatable impeller 4 is arranged, wherein the impeller 4 has a plurality of circumferentially spaced apart blades 4a, and wherein the impeller 4 is rotatably mounted about a center of rotation 4b. In the center of the liquid ring compressor 1 a fixed inlet and outlet device 6 is arranged, which has two circumferentially extending inlet openings 7 and two circumferentially extending outlet openings 8. The inlet and outlet device 6 is also referred to as internal distributor. The liquid ring compressor 1 is configured in the illustrated embodiment as a double-flow pump by having these two inlet openings 7, two outlet openings 8 and also two mutual compression spaces 10a. The interior 2a is bounded in the circumferential direction by a housing inner wall 3, which surrounds the impeller 4 in the circumferential direction from the outside, wherein the housing inner wall 3 is aligned to the impeller 4 out. The housing inner wall 3 comprises a plurality of subsections 3a - 3n, which together form the in Form the circumferential direction of the housing inner wall 3. In the interior 2a is a liquid which is conveyed by the impeller 4 in the direction of rotation 5, and which forms a liquid ring 9 with a boundary line 9a. The space between the boundary line 9a and the inlet and outlet device 6 forms a delivery chamber 10, within which a gas is pumped from the inlet opening 7 to the outlet opening 8. As in FIG. 1 1, the delivery space 10 is divided in the circumferential direction into a plurality of sub-conveying spaces 10a which are successively delimited by a respective bucket 4a, wherein the volume of the sub-conveying spaces 10a increases in the area of the inlet opening 7 in the direction 9b and thereby performs a suction movement, and wherein reduces the volume of the sub-conveying spaces 10a toward the outlet opening 8 in the direction 9c, whereby a compression movement is carried out. This pumping process takes place both in the FIG. 1 The conveying space 10 shown above on the left or the sub-conveying spaces 10a and also in the conveying space 10 or the sub-conveying spaces 10a shown at the bottom right.

Im dargestellten Ausführungsbeispiel weist die Gehäuseinnenwand 3 einen ersten Teilabschnitt 3d und einen dritten Teilabschnitt 3f auf, welche konzentrisch zum Drehzentrum 4b des Schaufelrades 4 verlaufen und zum Drehzentrum 4b einen Abstand R beziehungsweise einen Exzentrizitätsradius Re, auch als Exzentrizitätskrümmungsradius Re bezeichnet, aufweisen. Ein zweiter Teilabschnitt 3e verläuft zwischen dem ersten Teilabschnitt 3d und dem dritten Teilabschnitt 3f. Ein vierter Teilabschnitt 3g verläuft zwischen dem dritten Teilabschnitt 3f und dem ersten Teilabschnitt 3d. Die Gehäuseinnenwand 3 weist an den Übergängen der Teilabschnitte 3d,3e,3f,3g jeweils eine Knickstelle K1, K2, K3, K4 auf. Diese können kantig, eckig oder auch abgerundet ausgestaltet sein. Der Flüssigkeitsringverdichter 1 weist ein ersten Zentrum 11a sowie ein zweites Zentrum 11b auf, welche bezüglich dem Drehzentrum 4b des Schaufelrades 4 um dieselbe Länge beabstandet sind. Die strichlierte Linie 11c zeigt einen Kreis mit erstem Zentrum 11a und Exzentrizitätsradius Re. Die strichlierte Linie 11d zeigt einen Kreis mit zweitem Zentrum 11b und Exzentrizitätsradius Re. Die Gehäuseinnenwand 3 weist zudem zwei gegenüberliegende Exzentrizitätspunkte 3h auf, an welchen die Gehäuseinnenwand 3 bezüglich dem Drehzentrum 4b den grössten Abstand aufweist. In einer vorteilhaften Ausgestaltung verläuft die Gehäuseinnenwand 3 entlang des zweiten Teilabschnittes 3e derart, dass der zweite Teilabschnitt 3e keine Knickstellen aufweist, und dass der zweite Teilabschnitt 3e Abschnitte mit unterschiedlichen Krümmungsradien aufweist. In der am meisten bevorzugten Ausgestaltung weist die Gehäuseinnenwand 3 entlang des zweiten Teilabschnittes 3e im Bereich des Öffnungspunktes 7a der Einlassöffnung 7 und /oder im Bereich des Schliesspunktes 8b der Auslassöffnung 8 Krümmungsradien Rl, Rk auf, die kleiner ist als der Exzentrizitätsradius Re, wogegen der zweite Teilabschnitt 3e dazwischen Krümmungsradien Rm, Ri aufweist, die grösser sind als der Exzentrizitätsradius Re. Diese Ausgestaltung des Verlaufs der Gehäuseinnenwand 3 hat zur Folge, dass die Saugbewegung 9b der Grenzlinie 9a vergrössert beziehungsweise verstärkt wird, und dass die Kompressionsbewegung 9c der Grenzlinie 9a vergrössert beziehungsweise verstärkt wird, was eine Vergrösserung der Pumpleistung des Flüssigkeitsringverdichters 1 zur Folge hat. Die Radien Ri, Rk, Rl, Rm können sich in Umfangsrichtung verändern. In einer weiteren vorteilhaften Ausgestaltung kann jeder der Radien Ri, Rk, Rl, Rm jedoch auch einen konstanten Wert aufweisen.In the illustrated embodiment, the housing inner wall 3 has a first section 3d and a third section 3f, which run concentric to the center of rotation 4b of the impeller 4 and the center of rotation 4b a distance R or a radius of excision R e , also referred to as Exzentrizitätskrümmungsradius R e . A second subsection 3e extends between the first subsection 3d and the third subsection 3f. A fourth subsection 3g extends between the third subsection 3f and the first subsection 3d. The housing inner wall 3 has at the transitions of the sections 3d, 3e, 3f, 3g each have a kink K1, K2, K3, K4 on. These can be edged, angular or rounded. The liquid ring compressor 1 has a first center 11a and a second center 11b, which are spaced by the same length with respect to the center of rotation 4b of the impeller 4. The dashed line 11c shows a circle with first center 11a and eccentricity radius R e . The dashed line 11d shows a circle with the second center 11b and the eccentricity radius R e . The housing inner wall 3 also has two opposite eccentricity points 3h, at which the housing inner wall 3 has the greatest distance with respect to the center of rotation 4b. In an advantageous embodiment, the housing inner wall 3 runs along the second part section 3e such that the second part section 3e has no kinks, and that the second part section 3e has sections with different radii of curvature. In the most preferred embodiment, the housing inner wall 3 along the second portion 3e in the region of the opening point 7a of the inlet opening 7 and / or in the region of the closing point 8b of the outlet opening 8 radii of curvature Rl, Rk, which is smaller than the eccentricity radius R e , whereas the second section 3e has therebetween radii of curvature Rm, Ri which are greater than the radius of excision R e . This configuration of the course of the housing inner wall 3 has the consequence that the suction movement 9b of the boundary line 9a is increased or increased, and that the compression movement 9c of the boundary line 9a is increased or amplified, resulting in an increase in the pumping capacity of the liquid ring compressor 1 result. The radii Ri, Rk, Rl, Rm can vary in the circumferential direction. In a further advantageous embodiment, however, each of the radii Ri, Rk, Rl, Rm may also have a constant value.

Figur 2 zeigt in einem Schnitt senkrecht zur Drehachse 4b ein weiteres Ausführungsbeispiel eines Flüssigkeitsringverdichters 1 mit Gehäuse 2 und Gehäuseinnenwand 3, wobei die Flüssigkeitsringpump 1 ausser Betrieb ist und sich deshalb im Innenraum des Flüssigkeitsringverdichters 1 kein Fluid befindet. Der Flüssigkeitsringverdichter 1 weist, wie bereit in Figur 1 beschrieben, eine Gehäuseinnenwand 3 mit in Umfangsrichtung nacheinander verlaufend angeordnetem ersten, zweite, dritten und vierten Teilabschnitt 3d,3e,3f,3g und dazwischen angeordneten Knickstellen beziehungsweise Übergangsbereiche K1,K2,K3,K4 auf. In diesem Ausführungsbeispiel weisen im Teilabschnitt 3e alle vier Radien Ri, Rk, Rl, Rm einen konstanten Wert auf. Die beiden Radien Rm und Ri sind grösser als der Exzentrizitätsradius Re, wogegen die beiden Radien Rk und Rl kleiner sind als der Exzentrizitätsradius Re. In einer bevorzugten Ausgestaltung weist der Teilabschnitt 3e keine Knickstellen auf, was bedeutet, dass die Teilabschnitte mit Radien Rl, Rm, Ri, Rk an deren Übergangsstellen u 1, 3h und u4 in Drehrichtung 5 gegenseitig tangential verlaufen, sodass diese Übergangsstellen u 1, 3h und u4 keinen Knick beziehungsweise keine Unstetigkeit aufweisen. FIG. 2 shows in a section perpendicular to the axis of rotation 4b, a further embodiment of a liquid ring compressor 1 with housing 2 and housing inner wall 3, wherein the liquid ring pump 1 is out of operation and therefore in the interior of the liquid ring compressor 1 no fluid. The liquid ring compressor 1 has, as ready in FIG. 1 described, a housing inner wall 3 with circumferentially successively arranged first, second, third and fourth section 3d, 3e, 3f, 3g and arranged therebetween kinks or transition areas K1, K2, K3, K4. In this exemplary embodiment, all four radii Ri, Rk, Rl, Rm in the subsection 3e have a constant value. The two radii Rm and Ri are larger than the eccentricity radius R e , whereas the two radii Rk and Rl are smaller than the eccentricity radius R e . In a preferred embodiment, the portion 3e no kinks, which means that the sections with radii Rl, Rm, Ri, Rk at their transition points u 1, 3h and u4 in the direction of rotation 5 are mutually tangential, so that these transition points u 1, 3h and u4 have no kink or discontinuity.

Figur 3 zeigt eine Detailansicht des linken oberen Teils der in Figur 2 dargestellten Flüssigkeitsringverdichters 1. Der zweite Teilabschnitt 3e umfasst die folgenden vier in Drehrichtung 5 nacheinander folgenden Abschnitte, einen siebten Teilabschnitt 31 mit Krümmungsradius Rl, einen achten Teilabschnitt 3m mit Krümmungsradius Rm, welcher nach der Übergangsstelle u4 folgt, einen fünften Teilabschnitt 3i mit Krümmungsradius Ri, welcher nach dem Exzentrizitätspunkt 3h folgt, und einem sechsten Teilabschnitt 3k mit Krümmungsradius Rk, welcher nach der Übergangsstelle u 1 folgt. In einer vorteilhaften Ausgestaltung verläuft der zweite Teilabschnitt 3e spiegelsymmetrisch bezüglich einer durch die Punkte 3h und 4b verlaufenden Achse. Die Kreisbahn K stellt die durch die Aussenkante (4c) der Schaufeln 4a des Schaufelrades 4 beschriebenen Kreises dar. Der Abstand A zwischen der Kreisbahn K und der Gehäuseinnenwand 3 nimmt ausgehend vom Bereich des Öffnungspunktes 7a der Einlassöffnung 7 in Drehrichtung 5 zu, und weist im Exzentrizitätspunkt 3h den grössten Wert A1 auf. Der Abstand A reduziert sich daraufhin bis zum Bereich des Schliesspunktes 8b der Auslassöffnung 8. Figur 3 zeigt auch die Kreislinie 11c, welche durch eine Kreis mit Exzentrizitätsradius Re und dem ersten Zentrum 11a definiert ist. Die Gehäuseinnenwand 3 verläuft nun entlang des fünften und sechsten Teilabschnittes 3i, 3k derart, dass der Krümmungsradius Ri einen grösseren Wert aufweist als der Exzentrizitätsradius Re, sodass sich der fünfte Teilabschnitt 3i weiter von der Kreislinie 11c entfernt, und dass der Krümmungsradius Rk einen kleineren Wert aufweist als der Exzentrizitätsradius Re, sodass sich der sechste Teilabschnitt 3k der Kreislinie 11c wieder annähert. Der sechste Teilabschnitt 3k ist in einer vorteilhaften Ausgestaltung wie in Figur 3 dargestellt entlang der Auslassöffnung 8 verlaufend angeordnet, um durch den Verlauf der Gehäuseinnenwand 3 entlang des sechsten Teilabschnittes 3k eine erhöhte Kompressionsbewegung 9c auf den Flüssigkeitsring 9 beziehungsweise auf dessen Grenzlinie 9a zu bewirken, um dadurch die Förderwirkung zur Auslassöffnung 8 hin zu erhöhen. FIG. 3 shows a detail view of the left upper part of in FIG. 2 The second section 3e comprises the following four sections successively in the direction of rotation 5, a seventh section 31 with radius of curvature R1, an eighth section 3m with radius of curvature Rm, which follows the junction u4, a fifth section 3i with radius of curvature Ri, which follows after the eccentricity point 3h, and a sixth Subsection 3k with radius of curvature Rk, which follows after the transition point u 1. In an advantageous embodiment, the second section 3e is mirror-symmetrical with respect to an axis passing through the points 3h and 4b. The circular path K represents the circle described by the outer edge (4c) of the blades 4a of the blade wheel 4. The distance A between the circular path K and the housing inner wall 3 increases from the region of the opening point 7a of the inlet opening 7 in the direction of rotation 5, and points in Eccentricity point 3h the highest value A1. The distance A then reduces to the region of the closing point 8b of the outlet opening eighth FIG. 3 also shows the circular line 11c, which is defined by a circle with eccentricity radius R e and the first center 11a. The housing inner wall 3 now runs along the fifth and sixth subsection 3i, 3k in such a way that the radius of curvature Ri has a greater value than the eccentricity radius R e , so that the fifth subsection 3i moves further away from the circular line 11c, and that the radius of curvature Rk is smaller Has value as the eccentricity radius R e , so that the sixth portion 3k of the circular line 11c approaches again. The sixth section 3k is in an advantageous embodiment as in FIG. 3 represented along the outlet opening 8 arranged to effect through the course of the housing inner wall 3 along the sixth section 3k an increased compression movement 9c on the liquid ring 9 or on its boundary line 9a, thereby increasing the conveying effect to the outlet port 8 out.

Figur 4 zeigt ein weiters Ausführungsbeispiel eines Verlaufs der Gehäuseinnenwand 3. Im Wesentlichen ist die linke Hälfte des zweiten Teilabschnittes 3e dargestellt, welche einen fünften Teilabschnitt 3i und einen sechsten Teilabschnitt 3k umfasst. Der fünfte Teilabschnitt 3i weist einen Krümmungsradius Ri mit Drehzentrum zi auf. Der sechste Teilabschnitt 3k weist einen Krümmungsradius Rk mit Drehzentrum zk auf. Die Radien Ri,Rk und die Drehzentren zi,zk sind derart bemessen und angeordnet, dass die Tangenten des fünften und sechsten Teilabschnittes 3i,3k an der Übergangsstelle u 1 identisch sind, sodass die Übergangsstelle u1 keinen Knick beziehungsweise keine Unstetigkeit aufweist. Zum besseren Verständnis ist in Figur 4 zudem noch strichliert die Kreislinie 11c mit Exzentrizitätsradius Re und Drehzentrum 11a dargestellt, sowie strichliert die Kreislinie 4c mit Drehzentrum 4b des Schaufelrades 4 und mit Exzentrizitätsradius Re. Die beiden Krümmungsradien Ri, Rk weisen im dargestellten Ausführungsbeispiel einen konstanten Wert auf, wobei Ri grösser als R ist und wobei Rk kleiner als R ist. Die Radien Ri,Rk und die Drehzentren zi,zk können in einer Vielzahl von Möglichkeiten bemessen und angeordnet sein, derart, dass die Tangenten des fünften und sechsten Teilabschnittes 3i,3k an der Übergangsstelle u 1 identisch sind. Die Krümmungsradien Ri, Rk könnten in Drehrichtung 5 jedoch auch variierende Werte aufweisen, vorzugsweise derart, dass die Radien Ri grösser sind als R und dass die Radien Rk kleiner sind als R, und vorzugsweise derart, dass die Tangenten des fünften und sechsten Teilabschnittes 3i,3k an der Übergangsstelle u 1 identisch sind. FIG. 4 shows a further embodiment of a course of the housing inner wall 3. Essentially, the left half of the second section 3e is shown, which is a fifth Part 3i and a sixth section 3k includes. The fifth section 3i has a radius of curvature Ri with a center of rotation zi. The sixth section 3k has a radius of curvature Rk with a center of rotation zk. The radii Ri, Rk and the centers of rotation zi, zk are dimensioned and arranged such that the tangents of the fifth and sixth part sections 3i, 3k are identical at the transition point u 1, so that the transition point u1 has no kink or discontinuity. For better understanding is in FIG. 4 Moreover, even the circle shown by dashed lines 11c Exzentrizitätsradius R e and the rotational center 11a, and the dashed circular line 4c with the center of rotation 4b of the impeller 4 and R Exzentrizitätsradius e. The two radii of curvature Ri, Rk have a constant value in the illustrated embodiment, wherein Ri is greater than R and wherein Rk is less than R. The radii Ri, Rk and the centers of rotation zi, zk can be dimensioned and arranged in a variety of ways, such that the tangents of the fifth and sixth sections 3i, 3k are identical at the transition point u 1. However, the radii of curvature Ri, Rk could also have varying values in the direction of rotation 5, preferably such that the radii Ri are greater than R and that the radii Rk are smaller than R, and preferably such that the tangents of the fifth and sixth part sections 3i, 3k are identical at the transition point u 1.

Figur 5 zeigt eine Teilansicht eines Schnittes durch den in Figur 1 dargestellten Flüssigkeitsringverdichter 1 entlang der Schnittlinie B-B. Daraus ist der Verlauf des Schaufelrades 4 mit Schaufel 4a innerhalb des Gehäuses 2 ersichtlich. FIG. 5 shows a partial view of a section through the in FIG. 1 shown liquid ring compressor 1 along the section line BB. From this, the course of the blade wheel 4 with blade 4a within the housing 2 can be seen.

Claims (10)

  1. A liquid ring compressor (1) comprising a ring housing (2) as well as an impeller (4), wherein the impeller (4) is arranged within the ring housing (2) and is rotatably supported about an axis of rotation (4b) and in a direction of rotation (5), wherein the impeller (4) has a plurality of vanes (4a) arranged spaced apart from one another in the direction of rotation (5), and wherein the ring housing (2) has an inner housing wall (3) extending in the circumferential direction and aligned with respect to the impeller (4), characterized in that the inner housing wall (3) has a first part section (3d) and a third part section (3f) which extend curved with respect to the axis of rotation (4b), preferably circularly, and extend with an eccentric radius of curvature (Re) and which are arranged extending mutually symmetrically and lying opposite with respect to the axis of rotation (4b), and wherein the inner housing wall (3) has a second part section (3e) which connects the first part section (3d) to the third part section (3f); and wherein the second part section (3e) has a point of eccentricity (3h) between the first part section (3d) and the third part section (3f) which point of eccentricity has a maximum spacing (A1) having regard to a circular track (K) defined by the outer edges (4c) of the vanes (4a) in the radial direction with respect to the axis of rotation (4b); and wherein the second part section (3e) is composed of a fifth and sixth part section (3i, 3k) between the point of eccentricity (3h) and the third part section (3f) in the direction of rotation (5), wherein the fifth part section (3i) has a curved extent having radii of curvature (Ri) which are larger than the eccentric radius of curvature (Re) of the first part section (3d); and wherein the sixth part section (3k) has a curved extent having radii of curvature (Rk) which are smaller than the eccentric radius of curvature (Re) of the first part section (3d), and wherein the fifth and the sixth part section (3i, 3k) extend mutually tangentially at their transition point (U1), and wherein an inlet and outlet apparatus (6) is arranged within the ring housing (2), the inlet and outlet apparatus having an outlet opening (8); and wherein the outlet opening (8) extends in the direction of rotation (5) within the region between the point of eccentricity (3h) and the third part section (3f).
  2. A liquid ring compressor (1) in accordance with claim 1, characterized in that the fifth part section (3i) has a constant radius of curvature (Ri) and/or in that the sixth part section (3k) has a constant radius of curvature (Rk).
  3. A liquid ring compressor (1) in accordance with one of the preceding claims, characterized in that the outlet opening (8) extends along the same angular region as the sixth part section (3k).
  4. A liquid ring compressor (1) in accordance with any one of the preceding claims, characterized in that the second part section (3e) is composed of a seventh and an eighth part section (31, 3m) in the direction of rotation (5) between the first part section (3d) and the point of eccentricity (3h), wherein the seventh part section (31) has a curved extent having radii of curvature (Rl) which are smaller than the eccentric radius of curvature (3e) of the first part section (3d), and wherein the eighth part section (3m) has a curved extent having radii of curvature (Rm) which are larger than the eccentric radius of curvature (Re) of the first part section (3d), and wherein the seventh and the eighth part sections (31, 3m) extend mutually tangentially at their transition point (U2).
  5. A liquid ring compressor (1) in accordance with claim 4, characterized in that the seventh part section (31) has a constant radius of curvature (Rl) and/or in that the eighth part section (3m) has a constant radius of curvature (Rm).
  6. A liquid ring compressor (1) in accordance with one of the claims 4 or 5, characterized in that the eighth and the fifth part sections (3m, 3i) extend mutually tangentially at their transition point, the point of eccentricity (3h).
  7. A liquid ring compressor in accordance with one of the claims 1 or 2, characterized in that the second part section (3e) constantly has the same radius of curvature in the direction of rotation (5) between the first part section (3d) and the point of eccentricity (3h).
  8. A liquid ring compressor in accordance with any one of the claims 1 to 3, characterized in that the radius of curvature of the second part section (3e) corresponds to the eccentric radius of curvature (3e) of the first part section (3d) in the direction of rotation (5) between the first part section (3d) and the point of eccentricity (3h).
  9. A liquid ring compressor in accordance with the any one of the preceding claims, characterized in that the transition from the sixth part section (3k) to the third part section (3f) has a kink point (K1).
  10. A liquid ring compressor in accordance with any one of the preceding claims, characterized in that the inner housing wall (3) has a fourth part section (3g) which) connects the third part section (3f) to the first part section (3d) in the direction of rotation (5), and in that the fourth part section (3g) extends rotationally symmetrical to the second part section (3e) with respect to the axis of rotation (4b).
EP20110186724 2011-10-26 2011-10-26 Liquid ring compressor Active EP2587065B1 (en)

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GB2540754A (en) * 2015-07-22 2017-02-01 Edwards Ltd Abatement system
CN118378314B (en) * 2024-06-24 2024-08-20 淄博真空设备厂有限公司 Design method of liquid ring compressor impeller

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DE1021976B (en) * 1951-02-15 1958-01-02 Nash Engineering Co Liquid ring gas pump
FR1388967A (en) * 1964-01-02 1965-02-12 Improvements to gas pumps and liquid ring compressors
US5213479A (en) 1992-04-09 1993-05-25 The Nash Engineering Company Liquid ring pumps with improved housing shapes

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