EP0401397A1 - Liquid-ring compressor - Google Patents

Liquid-ring compressor Download PDF

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Publication number
EP0401397A1
EP0401397A1 EP89110169A EP89110169A EP0401397A1 EP 0401397 A1 EP0401397 A1 EP 0401397A1 EP 89110169 A EP89110169 A EP 89110169A EP 89110169 A EP89110169 A EP 89110169A EP 0401397 A1 EP0401397 A1 EP 0401397A1
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EP
European Patent Office
Prior art keywords
pressure
compressor
liquid ring
additional openings
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.)
Granted
Application number
EP89110169A
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German (de)
French (fr)
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EP0401397B1 (en
Inventor
Peter Dipl.-Ing. Trimborn
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Siemens AG
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Siemens AG
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Application filed by Siemens AG filed Critical Siemens AG
Priority to DE8989110169T priority Critical patent/DE58902779D1/en
Priority to EP89110169A priority patent/EP0401397B1/en
Priority to AT89110169T priority patent/ATE82620T1/en
Priority to FI902195A priority patent/FI902195A0/en
Priority to US07/527,012 priority patent/US5073089A/en
Priority to JP1990058402U priority patent/JPH035996U/ja
Priority to CA002018032A priority patent/CA2018032A1/en
Publication of EP0401397A1 publication Critical patent/EP0401397A1/en
Publication of EP0401397B1 publication Critical patent/EP0401397B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F04C19/005—Details concerning the admission or discharge
    • F04C19/007—Port members in the form of side plates

Definitions

  • the invention relates to a liquid ring compressor according to the preamble of claim 1.
  • Such a liquid ring compressor is known from DE-C-32 10 161.
  • a plurality of additional openings of the same size designed as slots are provided in front of the pressure opening.
  • the invention is therefore based on the object of developing a liquid ring compressor according to the preamble of claim 1 in such a way that the pressure losses of the type mentioned above are further reduced.
  • the additional openings In the case of a liquid ring compressor with a flat control disk, it is particularly advantageous for the additional openings to extend in the radial direction up to the liquid ring extend that the envelope curve over the radially outer ends of the additional openings corresponds at least approximately to the course of the liquid ring which occurs at the nominal pressure ratio of the compressor. As a result, better compatibility of liquid-side liquid conveyance is also achieved. Excess liquid can be expelled through the additional openings reaching to the liquid ring even before the actual pressure opening, so that there are no longer any undesirable pressures causing loss of performance in the area of the apex of the compressor.
  • the desired dimensioning of the passage area of the additional openings is achieved in a liquid ring compressor with a conically shaped control element in that the additional openings are designed as straight-line slots, the length of which decreases towards the pressure opening.
  • the liquid ring compressor 1 shown in a partial section 2 denotes the compressor housing, which surrounds a blade wheel 5 which is offset eccentrically with respect to the housing axis 4 with its shaft axis 3.
  • the impeller 5 is mounted in bearing plates 6 attached to the compressor housing 2.
  • a suction and pressure port is arranged, of which only the suction port 7 is visible in the sectional view, for example.
  • a flat control disk 8 is inserted between the bearing plate 6 and the compressor housing 2.
  • This control disk 8 has at least one suction opening 9 and one pressure opening 10. Via these suction and pressure openings 9 and 10, the suction and pressure ports are connected to the respective vane chambers, which overlap with the suction and pressure openings 9 and 10.
  • gas can be sucked into the relevant blade chambers via the suction nozzle 7 and the suction opening 9 and gas can be expelled from the respective blade chambers via the pressure opening 10 and the pressure nozzle.
  • FIGS. 2 and 3 show several additional openings 12 are provided on the flat control disk 8 in relation to the compression direction (arrow 11) in front of the pressure opening 10. These additional openings 12 are covered on the side of the control disk 8 facing away from the impeller 5 by check valves. These check valves open the respective additional opening 12 as soon as there is a slightly higher pressure in the blade chamber passing by than at the pressure port. The gas compressed in the relevant vane chamber can thus flow out.
  • the additional openings 12 are formed in the radial direction with different lengths, the length of the additional openings 12 decreasing towards the pressure opening 10.
  • additional openings 12 thus have a passage area that decreases towards the pressure opening, since their width remains constant and is only slightly wider or equal to or smaller than the thickness of the blades of the blade rades 5 is dimensioned.
  • the additional openings 12 are adapted in their radial course to the radial course of the blades, so that the respective additional opening 12 is completely covered when a blade passes by. In this way, backflows through the additional openings 12 between two different blade chambers can be avoided.
  • the additional openings 12 are dimensioned in their radial length such that they extend with their radially outer end 16 up to the course 13 or 14 or 15 of the liquid ring which is set in accordance with the nominal pressure ratio of the liquid ring compressor. This achieves a maximum passage area for each individual additional opening 12 as well as a maximum total passage area for the additional openings 12 released by the check valves at the respective pressure conditions.
  • the passage area available in each case is therefore, in a first approximation, proportional to the gas mass present in the vane chambers, so that the pressure losses are substantially reduced as a result of this adaptation.
  • a cone-like control element 17 is provided instead of a flat control disk 8.
  • This control element extends coaxially to the shaft 18 of the compressor and engages under the impeller 19 over an axial partial length.
  • a suction and a pressure opening 9 and 10 are again provided on the conical surface 20 of this control element 17, as shown in the development according to FIG. 5, a suction and a pressure opening 9 and 10 are again provided on the conical surface 20 of this control element 17, as shown in the development according to FIG. 5, a suction and a pressure opening 9 and 10 are again provided.
  • a plurality of additional openings 22 are connected upstream of the pressure opening.
  • the width 21 of these additional openings 22 is either slightly wider or the same or smaller than the thickness of the blades on the blade base, so that again a complete coverage of the individual additional openings 22 is achieved by the passing blades.
  • the individual additional openings 22 toward the pressure opening 10 are shortened compared to the previous additional opening 22.
  • the necessary reduction in the passage area of the additional openings 22 closer to the pressure opening 10 is thus achieved.
  • the reduction from additional opening to additional opening is selected such that the total passage area of the additional openings 22, which are respectively released by the check valves, is approximately proportional to the gas mass present in the respective vane chambers.
  • the degree of reduction from additional opening to additional opening is determined by the nominal pressure ratio of the compressor.
  • each additional opening 22 opens into a channel 24 formed in the cone body 23 of the cone-shaped control element 17 against each other other delimited. A sufficient flow cross-section is available through these channels 24 for the gas mass to be discharged, so that no additional pressure losses occur.
  • this check valve consists of an elastic valve plate 27 resting on the outlet opening 26.
  • a catch plate 28 is arranged at a certain distance from the valve plate 27, against which the valve plate 27 comes into contact shown in dashed lines) when gas and / or liquid is expelled via the relevant additional opening 22 and the channel 24.
  • an arrangement is also possible in which the valve tongues protrude into the cone and directly cover the additional openings. This eliminates the gas-filled space between the additional openings and the valve tongues, in accordance with the arrangement shown in FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Acyclic And Carbocyclic Compounds In Medicinal Compositions (AREA)

Abstract

The invention relates to a liquid-ring compressor with a housing (2) enclosing a blade wheel (5), on the end faces of which housing end plates (6) are arranged in which the blade wheel (5) is eccentrically supported in relation to the housing (2), on at least one end plate (6) of which compressor an intake and a pressure connection are provided and between this end plate (6) and the blade wheel (5) a control element (8 or 17) is provided which has at least one intake aperture (9) for connecting the intake connection (7) to the particular blade chambers of the blade wheel (5) in the intake area, and a pressure aperture (10) for connecting the pressure connection to the particular blade chambers located in the compression area, together with a plurality of additional apertures (12 or 22) provided with non-return valves and situated upstream in relation to the compression direction (11) of the pressure aperture (10). On such a compressor a reduction of the pressure losses is achieved in that the passage cross-section of the individual additional apertures (12 or 22) is reduced in the direction of the pressure aperture (10) in such a way that the overall passage cross-section of the additional apertures (12 or 22) opened up by each of the non-return valves during the compression process is at least roughly proportional to the particular rated pressure ratio of the compressor (1) of the gaseous mass present in the blade chambers. <IMAGE>

Description

Die Erfindung betrifft einen Flüssigkeitsringverdichter gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a liquid ring compressor according to the preamble of claim 1.

Ein solcher Flüssigkeitsringverdichter ist durch die DE-C-32 10 161 bekannt. Bei diesem Verdichter sind vor der Drucköffnung mehrere, gleich große als Schlitze ausgebildete Zusatzöffnungen vorgesehen.Such a liquid ring compressor is known from DE-C-32 10 161. In the case of this compressor, a plurality of additional openings of the same size designed as slots are provided in front of the pressure opening.

Es hat sich gezeigt, daß es bei einer solchen Ausbildung der Zusatzöffnungen insbesondere bei höheren Ansaugdrücken und im Überdruckbereich, d.h. bei einem gegenüber dem Atmosphärendruck höheren Verdichtungsdruck, doch noch zu nennenswerten Druckver­lusten beim Durchströmen der Zusatzöffnungen kommt.It has been shown that with such a configuration of the additional openings, in particular at higher intake pressures and in the overpressure range, i.e. at a compression pressure that is higher than atmospheric pressure, but there is still significant pressure loss when flowing through the additional openings.

Der Erfindung liegt daher die Aufgabe zugrunde, einen Flüssig­keitsringverdichter gemäß dem Oberbegriff des Anspruchs 1 so weiterzubilden, daß die Druckverluste der vorstehend genannten Art weiter reduziert werden.The invention is therefore based on the object of developing a liquid ring compressor according to the preamble of claim 1 in such a way that the pressure losses of the type mentioned above are further reduced.

Die Lösung der gestellten Aufgabe gelingt durch die im Kenn­zeichen des Anspruchs 1 angegebenen Merkmale. Durch die be­schriebene Bemessung der Durchtrittsfläche der einzelnen Zusatzöffnungen steht an jeder Stelle des Auslaßbereiches eine jeweils den an dieser Stelle vorliegenden Verhältnissen (Gas­masse, Verdichtungsdruck) entsprechende Durchtrittsfläche zur Verfügung, so daß sich nur noch minimale Verluste ergeben.The problem is solved by the features specified in the characterizing part of claim 1. Due to the described dimensioning of the passage area of the individual additional openings, a passage area corresponding to the prevailing conditions (gas mass, compression pressure) is available at each point of the outlet area, so that there are only minimal losses.

Bei einem Flüssigkeitsringverdichter mit einer ebenen Steuer­scheibe ist es besonders vorteilhaft, daß sich die Zusatzöff­nungen in radialer Richtung derart bis zu dem Flüssigkeitsring erstrecken, daß die Hüllkurve über die radial außenliegenden Enden der Zusatzöffnungen zumindest angenähert dem sich bei dem Nenndruckverhältnis des Verdichters einstellenden Verlauf des Flüssigkeitsringes entspricht. Hierdurch wird ferner eine bessere Verträglichkeit von saugseitiger Flüssigkeitsmitförde­rung erreicht. Überschüssige Flüssigkeit kann durch die bis zum Flüssigkeitsring reichenden Zusatzöffnungen bereits vor der eigentlichen Drucköffnung ausgestoßen werden, so daß es im Bereich des Scheitelpunktes des Verdichters nicht mehr zu uner­wünschten, Leistungsverluste verursachenden Pressungen kommt.In the case of a liquid ring compressor with a flat control disk, it is particularly advantageous for the additional openings to extend in the radial direction up to the liquid ring extend that the envelope curve over the radially outer ends of the additional openings corresponds at least approximately to the course of the liquid ring which occurs at the nominal pressure ratio of the compressor. As a result, better compatibility of liquid-side liquid conveyance is also achieved. Excess liquid can be expelled through the additional openings reaching to the liquid ring even before the actual pressure opening, so that there are no longer any undesirable pressures causing loss of performance in the area of the apex of the compressor.

Die gewünschte Bemessung der Durchtrittsfläche der Zusatzöff­nungen wird bei einem Flüssigkeitsringverdichter mit einem konusförmig ausgebildeten Steuerelement dadurch erreicht, daß die Zusatzöffnungen als geradlinige Schlitze ausgebildet sind, deren Länge zur Drucköffnung hin abnimmt.The desired dimensioning of the passage area of the additional openings is achieved in a liquid ring compressor with a conically shaped control element in that the additional openings are designed as straight-line slots, the length of which decreases towards the pressure opening.

Anhand eines in der Zeichnung dargestellten Ausführungsbei­spieles wird der Anmeldungsgegenstand nachfolgend näher be­schrieben. Es zeigt:

  • FIG 1 in einem Teilschnitt einen Flüssigkeitsringverdichter mit einer ebenen Steuerscheibe,
  • FIG 2 eine für bestimmte Nenndruckverhältnisse ausgebildete ebene Steuerscheibe in Draufsicht,
  • FIG 3 eine für ein anderes Nenndruckverhältnis ausgebildete ebene Steuerscheibe in Draufsicht,
  • FIG 4 in einem Teilschnitt einen Flüssigkeitsringverdichter mit einem konusförmig ausgebildeten Steuerelement,
  • FIG 5 ein konusförmiges Steuerelement in abgewickelter Darstellung,
  • FIG 6 ein konusförmiges Steuerelement in Stirnansicht,
  • FIG 7 einen Teilschnitt des konusförmigen Steuerelementes entlang der Linie VII-VII in FIG 6.
The subject of the application is described in more detail below using an exemplary embodiment shown in the drawing. It shows:
  • 1 shows a partial section of a liquid ring compressor with a flat control disk,
  • 2 shows a planar control disk designed for certain nominal pressure ratios in plan view,
  • 3 shows a planar control disk designed for a different nominal pressure ratio in plan view,
  • 4 shows a partial section of a liquid ring compressor with a conical control element,
  • 5 shows a conical control element in a developed representation,
  • 6 shows a conical control element in front view,
  • 7 shows a partial section of the conical control element along the line VII-VII in FIG. 6.

Bei dem in einem Teilschnitt dargestellten Flüssigkeitsring­verdichter 1 ist mit 2 das Verdichtergehäuse bezeichnet, das ein mit seiner Wellenachse 3 exzentrisch gegenüber der Gehäuse­achse 4 versetztes Schaufelrad 5 umschließt. Die Lagerung des Schaufelrades 5 erfolgt in an dem Verdichtergehäuse 2 ange­bauten Lagerschilden 6. An dem in der Zeichnung dargestellten einen Lagerschild 6 ist jeweils ein Saug- und Druckstutzen angeordnet, von denen in der Schnittdarstellung beispielsweise nur der Saugstutzen 7 sichtbar ist. Zwischen dem Lagerschild 6 und dem Verdichtergehäuse 2 ist eine ebene Steuerscheibe 8 ein­gefügt. Diese Steuerscheibe 8 weist mindestens eine Saugöffnung 9 und eine Drucköffnung 10 auf. Über diese Saug- und Drucköff­nung 9 und 10 stehen der Saug- und der Druckstutzen mit den jeweiligen, sich mit der Saug- und Drucköffnung 9 und 10 deckenden Schaufelkammern in Verbindung. Dadurch kann über den Saugstutzen 7 und die Saugöffnung 9 Gas in die betreffenden Schaufelkammern eingesaugt und über die Drucköffnung 10 und den Druckstutzen Gas aus den jeweiligen Schaufelkammern ausgestoßen werden.In the case of the liquid ring compressor 1 shown in a partial section, 2 denotes the compressor housing, which surrounds a blade wheel 5 which is offset eccentrically with respect to the housing axis 4 with its shaft axis 3. The impeller 5 is mounted in bearing plates 6 attached to the compressor housing 2. On the one bearing plate 6 shown in the drawing, a suction and pressure port is arranged, of which only the suction port 7 is visible in the sectional view, for example. A flat control disk 8 is inserted between the bearing plate 6 and the compressor housing 2. This control disk 8 has at least one suction opening 9 and one pressure opening 10. Via these suction and pressure openings 9 and 10, the suction and pressure ports are connected to the respective vane chambers, which overlap with the suction and pressure openings 9 and 10. As a result, gas can be sucked into the relevant blade chambers via the suction nozzle 7 and the suction opening 9 and gas can be expelled from the respective blade chambers via the pressure opening 10 and the pressure nozzle.

Wie die Darstellung in den FIG 2 und 3 zeigt, sind an der ebenen Steuerscheibe 8 in bezug auf die Verdichtungsrichtung (Pfeil 11) vor der Drucköffnung 10 mehrere Zusatzöffnungen 12 vorgesehen. Diese Zusatzöffnungen 12 sind auf der dem Schaufel­rad 5 abgewandten Seite der Steuerscheibe 8 durch Rückschlag­ventile abgedeckt. Diese Rückschlagventile geben die jeweilige Zusatzöffnung 12 frei, sobald in der an ihr vorbeistreichenden Schaufelkammer ein geringfügig höherer Druck als am Druck­stutzen herrscht. Damit kann das in der betreffenden Schaufel­kammer verdichtete Gas ausströmen. Die Zusatzöffnungen 12 sind in radialer Richtung mit unterschiedlicher Länge ausgebildet, wobei die Länge der Zusatzöffnungen 12 zu der Drucköffnung 10 hin abnimmt. Damit weisen diese Zusatzöffnungen 12 eine zur Drucköffnung hin abnehmende Durchtrittsfläche auf, da nämlich ihre Breite konstant bleibt und nur geringfügig breiter bzw. gleich oder kleiner als die Dicke der Schaufeln des Schaufel­ rades 5 bemessen ist. Desgleichen sind die Zusatzöffnungen 12 in ihrem radialen Verlauf dem radialen Verlauf der Schaufeln angepaßt, so daß beim Vorbeistreichen einer Schaufel die jewei­lige Zusatzöffnung 12 vollständig abgedeckt wird. Auf diese Weise lassen sich Rückströmungen über die Zusatzöffnungen 12 zwischen zwei verschiedenen Schaufelkammern vermeiden.As the illustration in FIGS. 2 and 3 shows, several additional openings 12 are provided on the flat control disk 8 in relation to the compression direction (arrow 11) in front of the pressure opening 10. These additional openings 12 are covered on the side of the control disk 8 facing away from the impeller 5 by check valves. These check valves open the respective additional opening 12 as soon as there is a slightly higher pressure in the blade chamber passing by than at the pressure port. The gas compressed in the relevant vane chamber can thus flow out. The additional openings 12 are formed in the radial direction with different lengths, the length of the additional openings 12 decreasing towards the pressure opening 10. These additional openings 12 thus have a passage area that decreases towards the pressure opening, since their width remains constant and is only slightly wider or equal to or smaller than the thickness of the blades of the blade rades 5 is dimensioned. Likewise, the additional openings 12 are adapted in their radial course to the radial course of the blades, so that the respective additional opening 12 is completely covered when a blade passes by. In this way, backflows through the additional openings 12 between two different blade chambers can be avoided.

Mit 13,14 und 15 ist in den FIG 2 und 3 der sich bei verschie­denen Nenndruckverhältnissen einstellende Verlauf des Flüssig­keitsringes in dem Verdichter angedeutet. Bei einem Flüssig­keitsringverdichter mit einem niedrigen Nenndruckverhältnis, beispielsweise 2:1, ergibt sich der mit 13 bezeichnete Verlauf. Ein Verdichter mit einem mittleren Nenndruckverhältnis von etwa 5:1 weist den mit 14 angedeuteten Verlauf des Flüssigkeits­ringes auf. Bei einem für hohe Druckverhältnisse ca. 30-40:1 ausgelegten Flüssigkeitsringverdichter stellt sich der mit 15 bezeichnete Verlauf des Flüssigkeitsringes ein.2, 3 indicate the course of the liquid ring in the compressor that occurs at different nominal pressure ratios. In the case of a liquid ring compressor with a low nominal pressure ratio, for example 2: 1, the course designated 13 results. A compressor with an average nominal pressure ratio of approximately 5: 1 has the course of the liquid ring indicated by 14. In the case of a liquid ring compressor designed for high pressure ratios of approximately 30-40: 1, the course of the liquid ring denoted by 15 is established.

Die Zusatzöffnungen 12 sind in ihrer radialen Länge so bemessen, daß sie sich mit ihrem radial außenliegenden Ende 16 bis zu dem sich entsprechend dem Nenndruckverhältnis des Flüssigkeitsring­verdichters einstellenden Verlauf 13 bzw.14 bzw.15 des Flüssig­keitsringes erstrecken. Hierdurch wird eine maximale Durch­trittsfläche sowohl für jede einzelne Zusatzöffnung 12 als auch eine maximale Gesamtdurchtrittsfläche für die bei den jeweili­gen Druckverhältnissen durch die Rückschlagventile freigegebenen Zusatzöffnungen 12 erreicht. Die jeweils zur Verfügung stehende Durchtrittsfläche ist damit in erster Näherung zu der in den Schaufelkammern vorhandenen Gasmasse proportional, so daß infolge dieser Anpassung die Druckverluste wesentlich vermin­dert sind.The additional openings 12 are dimensioned in their radial length such that they extend with their radially outer end 16 up to the course 13 or 14 or 15 of the liquid ring which is set in accordance with the nominal pressure ratio of the liquid ring compressor. This achieves a maximum passage area for each individual additional opening 12 as well as a maximum total passage area for the additional openings 12 released by the check valves at the respective pressure conditions. The passage area available in each case is therefore, in a first approximation, proportional to the gas mass present in the vane chambers, so that the pressure losses are substantially reduced as a result of this adaptation.

Dadurch, daß sich die Enden 16 der Zusatzöffnungen 12 bis zu dem eine Hüllkurve für diese Enden 16 bildenden Flüssigkeits­ring erstrecken, kann eventuell überschüssige Flüssigkeit bereits durch die von der Drucköffnung weiter entfernt liegen­den Zusatzöffnungen 12 ausgestoßen werden. Damit wird ein ent­sprechender Flüssigkeitsstau vor dem Scheitelpunkt des Ver­dichters und der damit verbundene Leistungsverlust vermieden.Because the ends 16 of the additional openings 12 extend as far as the liquid ring forming an envelope for these ends 16, excess liquid can possibly be are already ejected through the additional openings 12 which are further away from the pressure opening. This prevents a corresponding liquid build-up in front of the compressor's apex and the associated loss of performance.

Bei dem in der FIG 4 dargestellten Flüssigkeitsringverdichter 1 ist statt einer ebenen Steuerscheibe 8 ein konusartiges Steuer­element 17 vorgesehen. Dieses Steuerelement erstreckt sich koaxial zur Welle 18 des Verdichters und untergreift das Schaufelrad 19 auf einer axialen Teillänge. An der Konusfläche 20 dieses Steuerelementes 17 sind, wie die Abwicklung nach FIG 5 zeigt, wiederum je eine Saug- und eine Drucköffnung 9 und 10 vorgesehen. Der Drucköffnung sind mehrere Zusatzöffnungen 22 vorgeschaltet. Die Breite 21 dieser Zusatzöffnungen 22 ist entweder geringfügig breiter oder gleich bzw. kleiner als die Dicke der Schaufeln am Schaufelgrund gewählt, so daß wiederum eine vollständige Überdeckung der einzelnen Zusatzöffnungen 22 durch die vorbeistreichenden Schaufeln erreicht wird. In axia­ler Richtung sind die einzelnen Zusatzöffnungen 22 zu der Drucköffnung 10 hin gegenüber der jeweils vorhergehenden Zusatzöffnung 22 verkürzt. Damit wird die notwendige Verklei­nerung der Durchtrittsfläche der näher zur Drucköffnung 10 liegenden Zusatzöffnungen 22 erreicht. Die Verkleinerung von Zusatzöffnung zu Zusatzöffnung ist so gewählt, daß die Gesamt­durchtrittsfläche der jeweils durch die Rückschlagventile freigegebenen Zusatzöffnungen 22 der in den jeweiligen Schau­felkammern vorhandenen Gasmasse annähernd proportional ist. Durch das Nenndruckverhältnis des Verdichters wird das Maß der Verkleinerung von Zusatzöffnung zu Zusatzöffnung bestimmt.In the liquid ring compressor 1 shown in FIG. 4, a cone-like control element 17 is provided instead of a flat control disk 8. This control element extends coaxially to the shaft 18 of the compressor and engages under the impeller 19 over an axial partial length. On the conical surface 20 of this control element 17, as shown in the development according to FIG. 5, a suction and a pressure opening 9 and 10 are again provided. A plurality of additional openings 22 are connected upstream of the pressure opening. The width 21 of these additional openings 22 is either slightly wider or the same or smaller than the thickness of the blades on the blade base, so that again a complete coverage of the individual additional openings 22 is achieved by the passing blades. In the axial direction, the individual additional openings 22 toward the pressure opening 10 are shortened compared to the previous additional opening 22. The necessary reduction in the passage area of the additional openings 22 closer to the pressure opening 10 is thus achieved. The reduction from additional opening to additional opening is selected such that the total passage area of the additional openings 22, which are respectively released by the check valves, is approximately proportional to the gas mass present in the respective vane chambers. The degree of reduction from additional opening to additional opening is determined by the nominal pressure ratio of the compressor.

Wie aus den FIG 6 und 7 zu ersehen ist, mündet jede Zusatzöff­nung 22 in einen im Konuskörper 23 des konusförmigen Steuer­elementes 17 ausgebildeten Kanal 24. Die Kanäle 24 sind bis auf ihre auf der Stirnseite 25 des konusartigen Steuerelementes 17 liegende Auslaßöffnung 26 in sich geschlossen und gegenein­ ander abgegrenzt. Durch diese Kanäle 24 steht für die abzufüh­rende Gasmasse ein ausreichender Strömungsquerschnitt zur Ver­fügung, so daß keine zusätzlichen Druckverluste auftreten.As can be seen from FIGS. 6 and 7, each additional opening 22 opens into a channel 24 formed in the cone body 23 of the cone-shaped control element 17 against each other other delimited. A sufficient flow cross-section is available through these channels 24 for the gas mass to be discharged, so that no additional pressure losses occur.

Es besteht ferner die Möglichkeit die auf der Stirnseite 25 liegenden Auslaßöffnungen 26 durch ein Rückschlagventil abzu­decken. Gemäß der Darstellung in FIG 7 besteht dieses Rück­schlagventil aus einer auf der Auslaßöffnung 26 aufliegenden elastischen Ventilplatte 27. Um die Auslenkung der Ventil­platte 27 zu begrenzen, ist in einem bestimmten Abstand zu dieser eine Fangplatte 28 angeordnet, an der die Ventilplatte 27 zur Anlage kommt (gestrichelt dargestellt), wenn über die betreffende Zusatzöffnung 22 und den Kanal 24 Gas und/oder Flüssigkeit ausgestoßen wird. Anstelle der in FIG 7 darge­stellten Anordnung des Rückschlagventiles ist auch eine An­ordnung möglich, bei der die Ventilzungen in den Konus hinein­ragen und die Zusatzöffnungen direkt abdecken. Hierdurch ent­fällt der zwischen den Zusatzöffnungen und den Ventilzungen liegende, von Gas ausgefüllte Raum gemäß der in FIG 7 gezeig­ten Anordnung.There is also the possibility of covering the outlet openings 26 located on the end face 25 by means of a check valve. According to the illustration in FIG. 7, this check valve consists of an elastic valve plate 27 resting on the outlet opening 26. In order to limit the deflection of the valve plate 27, a catch plate 28 is arranged at a certain distance from the valve plate 27, against which the valve plate 27 comes into contact shown in dashed lines) when gas and / or liquid is expelled via the relevant additional opening 22 and the channel 24. Instead of the arrangement of the check valve shown in FIG. 7, an arrangement is also possible in which the valve tongues protrude into the cone and directly cover the additional openings. This eliminates the gas-filled space between the additional openings and the valve tongues, in accordance with the arrangement shown in FIG.

Mit einer solchen Ausgestaltung des konusartigen Steuerelemen­tes 17 gelingt eine stetige, feingestufte Anpassung an wech­selnde Verdichtungsverhältnisse trotz nur einer Konstruktions­form des Steuerelementes. Unterschiedliche Konusausführungen für unterschiedliche Druckverhältnisse sind nicht erforderlich.With such a configuration of the cone-like control element 17, a steady, finely graded adaptation to changing compression ratios succeeds despite only one design of the control element. Different cone designs for different pressure ratios are not required.

Claims (5)

1. Flüssigkeitsringverdichter, mit einem ein Schaufelrad (5) umgebenden Gehäuse (2), an dessen Stirnseiten Lagerschilde (6) angeordnet sind, in denen das Schaufelrad (5) exzentrisch gegenüber dem Gehäuse (2) gelagert ist, bei welchem Verdichter (1) mindestens an einem Lagerschild (6) je ein Saug- und Druck­stutzen und zwischen diesem Lagerschild (6) und dem Schaufel­rad (5) ein Steuerelement (8,17) vorgesehen ist, welches zur Verbindung des Saugstutzens (7) mit den sich jeweils im Ansaug­bereich befindlichen Schaufelkammern des Schaufelrades (5) mindestens eine Saugöffnung (9) und zur Verbindung des Druck­stutzens mit den sich jeweils im Verdichtungsbereich befind­lichen Schaufelkammern eine Drucköffnung (10) sowie mehrere in bezug auf die Verdichtungsrichtung der Drucköffnung (10) vorge­schaltete, mit Rückschlagventilen versehene Zusatzöffnungen (12 bzw. 22) aufweist,
dadurch gekennzeichnet,
daß in Richtung auf die Drucköffnung (10) hin die Durchtritts­fläche der einzelnen Zusatzöffnungen (12 bzw.22) derart ver­kleinert ist, daß die Gesamtdurchtrittsfläche der beim Verdich­tungsvorgang jeweils von den Rückschlagventilen freigegebenen Zusatzöffnungen (12 bzw.22) in bezug auf das jeweilige Nenn­druckverhältnis des Verdichters (1) der in den Schaufelkammern vorhandenen Gasmasse zumindest angenähert proportional ist.1. Liquid ring compressor, with a casing (2) surrounding a paddle wheel (5), on the end faces of which end shields (6) are arranged, in which the paddle wheel (5) is mounted eccentrically with respect to the housing (2), in which compressor (1) At least on one bearing plate (6) each has a suction and pressure port and between this bearing plate (6) and the paddle wheel (5) a control element (8, 17) is provided, which is used to connect the suction port (7) with each in the suction area located vane chambers of the vane wheel (5) at least one suction opening (9) and for connecting the pressure port to the vane chambers located in the compression area in each case one pressure opening (10) and several additional openings upstream with respect to the compression direction of the pressure opening (10) and provided with check valves ( 12 or 22),
characterized by
that in the direction of the pressure opening (10) the passage area of the individual additional openings (12 or 22) is reduced in such a way that the total passage area of the additional openings (12 or 22) released by the check valves during the compression process with respect to the respective nominal pressure ratio of the Compressor (1) is at least approximately proportional to the gas mass present in the blade chambers. 2. Flüssigkeitsringverdichter nach Anspruch 1, mit einem als ebene Steuerscheibe (8) ausgebildeten Steuerelement,
dadurch gekennzeichnet,
daß sich die Zusatzöffnungen (12) in radialer Richtung derart bis zu dem Flüssigkeitsring (13,14,15) erstrecken, daß die Hüllkurve über die radial außenliegenden Enden (16) der Zusatz­öffnungen (12) zumindest angenähert dem sich bei dem Nenndruck­verhältnis des Verdichters (1) einstellenden Verlauf (13,14,15) des Flüssigkeitsringes entspricht.2. Liquid ring compressor according to claim 1, with a control element designed as a flat control disk (8),
characterized by
that the additional openings (12) extend in the radial direction up to the liquid ring (13, 14, 15) in such a way that the envelope curve over the radially outer ends (16) of the additional openings (12) at least approximates that in the nominal pressure ratio of the compressor ( 1) corresponds to the setting course (13, 14, 15) of the liquid ring. 3. Flüssigkeitsringverdichter nach Anspruch 1, mit einem konus­artig ausgebildeten, die Welle (8) des Verdichters (1) auf einer axialen Teillänge konzentrisch umgebenden Steuerelement (17),
dadurch gekennzeichnet,
daß die Zusatzöffnungen (22) als geradlinige Schlitze ausgebil­det sind, deren Länge zur Drucköffnung (10) hin abnimmt.3. A liquid ring compressor according to claim 1, with a cone-shaped control element (17) concentrically surrounding the shaft (8) of the compressor (1) over an axial partial length,
characterized by
that the additional openings (22) are designed as rectilinear slots, the length of which decreases towards the pressure opening (10). 4. Flüssigkeitsringverdichter nach Anspruch 3,
dadurch gekennzeichnet,
daß jede Zusatzöffnung (22) in einen bis auf eine auf der Stirnseite (25) des konusförmigen Steuerelementes (17) liegende Auslaßöffnung (26) geschlossenen Kanal (24) mündet, die durch ein Rückschlagventil (27) abgedeckt ist.4. liquid ring compressor according to claim 3,
characterized by
that each additional opening (22) opens into a channel (24) which is closed except for an outlet opening (26) lying on the end face (25) of the conical control element (17) and which is covered by a check valve (27). 5. Flüssigkeitsringverdichter nach Anspruch 4,
dadurch gekennzeichnet,
daß das Rückschlagventil als Plattenventil (27) ausgebildet ist.5. liquid ring compressor according to claim 4,
characterized by
that the check valve is designed as a plate valve (27).
EP89110169A 1989-06-05 1989-06-05 Liquid-ring compressor Expired - Lifetime EP0401397B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DE8989110169T DE58902779D1 (en) 1989-06-05 1989-06-05 LIQUID RING COMPRESSOR.
EP89110169A EP0401397B1 (en) 1989-06-05 1989-06-05 Liquid-ring compressor
AT89110169T ATE82620T1 (en) 1989-06-05 1989-06-05 LIQUID RING COMPRESSORS.
FI902195A FI902195A0 (en) 1989-06-05 1990-05-02 VAETSKERINGKOMPRESSOR.
US07/527,012 US5073089A (en) 1989-06-05 1990-05-22 Liquid-ring compressor
JP1990058402U JPH035996U (en) 1989-06-05 1990-06-01
CA002018032A CA2018032A1 (en) 1989-06-05 1990-06-01 Liquid-ring compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP89110169A EP0401397B1 (en) 1989-06-05 1989-06-05 Liquid-ring compressor

Publications (2)

Publication Number Publication Date
EP0401397A1 true EP0401397A1 (en) 1990-12-12
EP0401397B1 EP0401397B1 (en) 1992-11-19

Family

ID=8201464

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89110169A Expired - Lifetime EP0401397B1 (en) 1989-06-05 1989-06-05 Liquid-ring compressor

Country Status (7)

Country Link
US (1) US5073089A (en)
EP (1) EP0401397B1 (en)
JP (1) JPH035996U (en)
AT (1) ATE82620T1 (en)
CA (1) CA2018032A1 (en)
DE (1) DE58902779D1 (en)
FI (1) FI902195A0 (en)

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WO1993003281A1 (en) * 1991-08-08 1993-02-18 Siemens Aktiengesellschaft Control unit for a liquid ring compressor
EP0645537A1 (en) * 1993-09-29 1995-03-29 The Nash Engineering Company check valve structures for liquid ring pumps
DE10121800C1 (en) * 2001-05-04 2002-08-22 Siemens Ag Liquid ring pump and control disc for a liquid ring pump

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GB2303879B (en) * 1995-08-01 1999-09-15 Hick Hargreaves & Co Ltd Liquid ring pump
US6354808B1 (en) * 2000-03-01 2002-03-12 The Nash Engineering Company Modular liquid ring vacuum pumps and compressors
JP5063010B2 (en) * 2006-02-16 2012-10-31 東光東芝メーターシステムズ株式会社 Gas flow meter and circuit unit for gas flow meter
JP2008102811A (en) * 2006-10-20 2008-05-01 Matsushita Electric Ind Co Ltd Gas control system
JP2008292115A (en) * 2007-05-28 2008-12-04 Tokyo Gas Co Ltd Gas blocking system, gas blocking method, and gas blocking program
US20110243761A1 (en) * 2010-03-31 2011-10-06 Rusty Darsey Pulsation Dampener for Gas Compressors Having Selectable Size Choke Openings
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

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US4521161A (en) * 1983-12-23 1985-06-04 The Nash Engineering Company Noise control for conically ported liquid ring pumps

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JPS555428A (en) * 1978-06-22 1980-01-16 Nakamura Suikan:Kk Water ring pump of side-air-port type
US4392783A (en) * 1980-12-12 1983-07-12 The Nash Engineering Company Liquid ring pump employing discharged pumping liquid for discharge port control
US4498844A (en) * 1983-08-08 1985-02-12 The Nash Engineering Company Liquid ring pump with conical or cylindrical port member
US4551070A (en) * 1983-12-23 1985-11-05 The Nash Engineering Company Noise control for conically ported liquid ring pumps
US4850808A (en) * 1985-03-19 1989-07-25 The Nash Engineering Company Liquid ring pump having port member with internal passageways for handling carry-over gas

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DE3210161C1 (en) * 1982-03-19 1983-10-06 Siemens Ag Liquid ring compressor for gases
US4521161A (en) * 1983-12-23 1985-06-04 The Nash Engineering Company Noise control for conically ported liquid ring pumps

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993003281A1 (en) * 1991-08-08 1993-02-18 Siemens Aktiengesellschaft Control unit for a liquid ring compressor
EP0645537A1 (en) * 1993-09-29 1995-03-29 The Nash Engineering Company check valve structures for liquid ring pumps
DE10121800C1 (en) * 2001-05-04 2002-08-22 Siemens Ag Liquid ring pump and control disc for a liquid ring pump

Also Published As

Publication number Publication date
US5073089A (en) 1991-12-17
EP0401397B1 (en) 1992-11-19
ATE82620T1 (en) 1992-12-15
DE58902779D1 (en) 1992-12-24
JPH035996U (en) 1991-01-21
CA2018032A1 (en) 1990-12-05
FI902195A0 (en) 1990-05-02

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