EP0644332A1 - Liquid ring gas pump with noise suppression device - Google Patents
Liquid ring gas pump with noise suppression device Download PDFInfo
- Publication number
- EP0644332A1 EP0644332A1 EP94114730A EP94114730A EP0644332A1 EP 0644332 A1 EP0644332 A1 EP 0644332A1 EP 94114730 A EP94114730 A EP 94114730A EP 94114730 A EP94114730 A EP 94114730A EP 0644332 A1 EP0644332 A1 EP 0644332A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- buffer space
- liquid ring
- gas pump
- ring gas
- pressure
- 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
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Classifications
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
- F04C29/0035—Equalization of pressure pulses
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
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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
Definitions
- the invention relates to a liquid ring gas pump according to the preamble of claim 1.
- the invention has for its object to dampen the noise of a liquid ring gas pump.
- the solution according to the invention consists in the features of claim 1.
- the effect of the buffer space adjoining the flow path is based on the fact that, by segregation of the gas-liquid mixture flowing past, it fills at least in its upper region with gas or a predominantly gas-containing gas-liquid mixture, while in the region in which the buffer space opens up towards the flow path specifically heavier gas-liquid mixture.
- the pressure and sound waves coming from the pressure slot of the delivery chamber and contained in the delivery flow are communicated to the medium contained in the buffer chamber, which is compressible thanks to the high gas content, while the specifically heavier component contained in the opening area of the buffer room forms an oscillating mass.
- the buffer space should have a certain minimum length in the vertical direction exhibit. It should be at least as long as far.
- the width of the geometric mean from its transverse dimensions in the area of its greatest extent can be seen. Its vertical length is expediently at least twice or even better three times as long.
- the width of the opening of the buffer space plays a significant role in relation to its length. This is expediently at least 1.5 times, expediently at least 2.5 times as large as the root from the cross-sectional area of the opening.
- the volume of the buffer space in relation to its opening width can also be important.
- the opening cross section is expediently not greater than 0.8 times, expediently than 0.5 times the square of the third root of the buffer space volume.
- the feature that the opening of the buffer space adjoins the flow path means that the buffer space should be so closely connected to the flow path that the transmission of vibrations to the buffer space is possible, but that the flow influence of the flow path on the buffer space is not so It is great that this prevents the formation of a substantially gas-filled or gas-enriched part in this room.
- the buffer space must have a certain minimum size in order to be effective. According to a first rule, it should not be less than 0.1 times, expediently 0.2 times the volume of the pressure space. According to another rule, it should be at least as large, expediently twice as large as the third power of the clear pressure nozzle diameter at the height of its connecting flange.
- a particularly simple form of the design of the buffer space is the insertion of one or more wall-forming parts, preferably ribs, in the pressure space of the pump. It is also advantageous if these are approximately perpendicular to the transverse plane of the housing, ie. H. be attached axially parallel. This simplifies installation or simplifies manufacture if the housing part is a casting.
- pressure openings which can be closed by valves are provided in addition to the constantly open pressure slot in the delivery chamber, special housing parts which require a certain space being provided for the formation or mounting of the valves. It can be difficult to create a buffer space in addition to the pressure space. According to the invention, this difficulty can be avoided or reduced by including the valve openings or at least some of them (namely preferably those which are first reached in the direction of rotation by the vanes of the impeller) in the buffer space. Only the gas-liquid mixture emerging from the constantly open part of the pressure slot or, if appropriate, the gas-liquid mixture emerging from the valve openings not included in the buffer space is then directed past the buffer space.
- the buffer space should be essentially closed in addition to its opening facing the flow path is nevertheless met because the valve openings (or at least the valve openings lying at the front in the direction of rotation) at those suction pressures at which the greatest noise development occurs. are closed for operational reasons.
- Another particularly simple form of the embodiment of the invention is when a double-walled pipe is led into the pressure chamber of the pump from the pressure port and closes the space between the two pipe walls at the top, but leaves it open at the bottom.
- the size of the buffer chamber opening should also have a certain minimum dimension in relation to the strength of the delivery flow, which is approximately represented by the cross-section of the discharge nozzle at the level of the connecting flange.
- the ratio of the size of the buffer space opening to this pressure port cross section should be between 0.2 and 5, preferably between 0.5 and 2.
- FIGS. II to VI illustrate advantageous exemplary embodiments in schematic cross sections.
- the pressure chamber 3 is in the left half of the housing.
- the gas-liquid mixture enters through the constantly open pressure slot 2 into the pressure chamber 3 and leaves it through the pressure port 1.
- the buffer chamber 4 is divided by walls 5 within the pressure chamber 3, which extends essentially vertically and whose vertical length is approximately twice as large like its greatest horizontal breadth.
- its walls 5 extend over the entire axial dimension of the pressure space between its boundary walls located in front of and behind the display plane or are closed by an additional wall running parallel to the display plane.
- the pressure openings 6, which can be closed by valves, open into the buffer space 4. In those operating areas in which the noise mainly arises, these openings are closed, the gas liquid stream emerging from the pressure slot 2 on its way to the pressure port 1 at the opening of the buffer space 4 located below is passed by.
- a buffer space is created around the pressure nozzle 1, which extends deeply into the pressure chamber 3, through the wall 5 and the housing wall located to the left of the pressure nozzle, the height of which is several times greater than the opening width shown in the illustration. Otherwise, the explanations for FIG. II can be transferred to this example.
- the buffer space is formed as an intermediate space between two concentric tubes, of which the interior forms the pressure connection.
- the pressure space extends over the entire cross section of the housing.
- a buffer space is formed by walls 5, the height of which is often greater than its greatest width, which appears in the plane of the illustration.
- a separating rib extending from the bottom upwards being arranged between the downward-facing opening of the buffer space and the constantly open pressure slot 2, which shields the buffer space opening from the pressure slot and ensures this that the delivery flow calms down and flows past it without any essential flow component directed into the buffer space.
Abstract
Description
Die Erfindung betrifft eine Flüssigkeitsringgaspumpe gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a liquid ring gas pump according to the preamble of
Beim Betrieb von Flüssigkeitsringgaspumpen werden durch die Pumpen selbst, insbesondere wenn sie aus Unterdruckbereichen ansaugen und gegen atmosphärischen Druck verdichten, mehr oder weniger starke Geräusche verursacht. Zum einen gibt es bei diesen Pumpen typische Kavitationsgeräusche, die vor allem dann auftreten, wenn sie bei relativer hohem Vakuum ansaugen (Diagramm Fig. 1, durchgezogene Linie).Es ist bekannt, sie durch Vermeidung der Kavitation zu bekämpfen, indem beispielsweise die kavitationsgefährdeten Stellen der Pumpe während des Fördervorgangs Gas zu geführt wird. Weitere Geräusche entstehen durch die periodische Arbeitsweise des Flügelrads und als Strömungsgeräusche. Sie entstehen bei einer als Vakuumpumpe betriebenen Flüssigkeitsringgaspumpe bei weniger tiefen Ansaugdrücken als die Kavitationsgeräusche und erreichen einen Höhepunkt bei Ansaugdrücken in der Größenordnung von 120 bis 200 mbar und nehmen dann mit ansteigendem Ansaugdrücken wieder ab. Man hat versucht, diese Geräusche dadurch zu dämpfen, daß man im Druckraum der Pumpe eine Trennwand vorsieht, die bis in den Teil des Druckraums hineinreicht, der bei normalem Förderstrom mit Flüssigkeit gefüllt ist bzw. ein stark mit Flüssigkeit angereichertes Gasflüssigkeitsgemisch enthält. Zwar erreicht man dadurch, daß das austretende Gasflüssigkeitsgemisch diesen Bereich durchströmen muß, eine gewisse Dämpfung (DE-C 2 036 295); aber in weiten Betriebsbereichen bleibt ein störender Geräuschpegel.When operating liquid ring gas pumps, the pumps themselves, particularly when they suck in from negative pressure areas and compress against atmospheric pressure, cause more or less strong noises. On the one hand, there are typical cavitation noises in these pumps, which occur especially when they are sucking in at a relatively high vacuum (diagram in Fig. 1, solid line) gas is supplied to the pump during the delivery process. Other noises arise from the periodic operation of the impeller and as flow noises. They arise in a liquid ring gas pump operated as a vacuum pump at lower suction pressures than the cavitation noises and peak at suction pressures of the order of 120 to 200 mbar and then take off again with increasing suction pressures from. Attempts have been made to dampen these noises by providing a partition in the pressure chamber of the pump which extends into the part of the pressure chamber which is filled with liquid during normal flow or contains a gas-liquid mixture which is highly enriched with liquid. A certain damping is achieved by the fact that the exiting gas-liquid mixture has to flow through this area (DE-C 2 036 295); but there is a disturbing noise level in wide operating areas.
Der Erfindung liegt die Aufgabe zugrunde, die Geräuschentwicklung einer Flüssigkeitsringgaspumpe zu dämpfen. Die erfindungsgemäße Lösung besteht in den Merkmalen des Anspruchs 1.The invention has for its object to dampen the noise of a liquid ring gas pump. The solution according to the invention consists in the features of
Die Wirkung des an den Strömungsweg angrenzenden Pufferraums beruht darauf, daß dieser sich durch Entmischung des vorbeiströmenden Gasflüssigkeitsgemisches zumindest in seinem oberen Bereich mit Gas oder einem überwiegenden gashaltigen Gasflüssigkeitsgemisch füllt, während sich in dem Bereich, im welchem sich der Pufferraum zum Strömungsweg hin öffnet, ein spezifisch schwereres Gasflüssigkeitsgemisch befindet. Die vom Druckschlitz des Förderraums herkommenden, im Förderstrom enthaltenen Druck- und Schallwellen werden dem im Pufferraum enthaltenen Medium mitgeteilt, das dank des hohen Gasanteils kompressibel ist, während der im Öffnungsbereich des Pufferraums enthaltene, spezifisch schwerere Anteil eine schwingende Masse bildet. Dadurch kommt eine Dämpfungswirkung ähnlich derjenigen eines Helmholtz-Resonators zustande. Demgemäß kann die Wirkung der Erfindung kurz dahin beschrieben werden, daß am Strömungsweg ein weitgehend mindestens mit Gas gefüllter Raum geschaffen wird, der für das vorbeiströmende Gasflüssigkeitsgemisch als Schalldämpfer wirkt.The effect of the buffer space adjoining the flow path is based on the fact that, by segregation of the gas-liquid mixture flowing past, it fills at least in its upper region with gas or a predominantly gas-containing gas-liquid mixture, while in the region in which the buffer space opens up towards the flow path specifically heavier gas-liquid mixture. The pressure and sound waves coming from the pressure slot of the delivery chamber and contained in the delivery flow are communicated to the medium contained in the buffer chamber, which is compressible thanks to the high gas content, while the specifically heavier component contained in the opening area of the buffer room forms an oscillating mass. This results in a damping effect similar to that of a Helmholtz resonator. Accordingly, the effect of the invention can be briefly described in that a largely at least gas-filled space is created on the flow path, which acts as a silencer for the gas-liquid mixture flowing past.
Damit der Pufferraum ein hinreichendes Gasvolumen aufnehmen kann, ohne daß dies durch die Strömungsbeeinflussung seitens des Förderstroms ständig wieder herausgespült wird, soll der Pufferraum eine bestimmte Mindestlänge in vertikaler Richtung aufweisen. Er soll mindestens so lang wie weit sein. Als Weite ist in diesem Zusammenhang das geometrische Mittel aus seinen Querabmessungen im Bereich seiner größten Ausdehnung anzusehen. Zweckmäßigerweise ist seine vertikale Länge mindestens doppelt oder noch besser dreimal so groß.So that the buffer space can hold a sufficient gas volume without this being constantly flushed out again by the flow influence on the part of the delivery flow, the buffer space should have a certain minimum length in the vertical direction exhibit. It should be at least as long as far. In this context, the width of the geometric mean from its transverse dimensions in the area of its greatest extent can be seen. Its vertical length is expediently at least twice or even better three times as long.
Eine beträchtliche Rolle spielt die Weite der Öffnung des Pufferraums im Verhältnis zu seiner Länge. Diese ist zweckmäßigerweise mindestens 1,5 mal, zweckmäßigerweise mindestens 2,5 mal so groß wie die Wurzel aus der Querschnittsfläche der Öffnung.The width of the opening of the buffer space plays a significant role in relation to its length. This is expediently at least 1.5 times, expediently at least 2.5 times as large as the root from the cross-sectional area of the opening.
Schließlich kann auch das Volumen des Pufferraums im Verhältnis zu seiner Öffnungsweite von Bedeutung sein. Zweckmäßigerweise ist der Öffnungsquerschnitt nicht größer als das 0,8-fache zweckmäßigerweise als das 0,5-fache Quadrat aus der dritten Wurzel des Pufferraumvolumens.Finally, the volume of the buffer space in relation to its opening width can also be important. The opening cross section is expediently not greater than 0.8 times, expediently than 0.5 times the square of the third root of the buffer space volume.
Das Merkmal, daß die Öffnung des Pufferraums an den Strömungsweg angrenzt, soll besagen, daß der Pufferraum zwar mit dem Strömungsweg so eng in Verbindung stehen soll, daß die Schwingungsübertragung zum Pufferraum hin möglich ist, daß aber der Strömungseinfluß des Strömungswegs auf den Pufferraum nicht so groß ist, daß dadurch die Bildung eines wesentlich gasgefüllten oder gasangereicherten Teils in diesem Raum verhindert wird.The feature that the opening of the buffer space adjoins the flow path means that the buffer space should be so closely connected to the flow path that the transmission of vibrations to the buffer space is possible, but that the flow influence of the flow path on the buffer space is not so It is great that this prevents the formation of a substantially gas-filled or gas-enriched part in this room.
Der Pufferraum muß eine gewisse Mindestgröße aufweisen, um wirksam zu sein. Nach einer ersten Regel soll er nicht kleiner sein als das 0,1-fache, zweckmäßigerweise das 0,2-fache Volumen des Druckraums. Nach einer anderen Regel soll er mindestens so groß sein, zweckmäßigerweise doppelt so groß sein wie die dritte Potenz des lichten Druckstutzendurchmessers in der Höhe von dessen Anschlußflansch.The buffer space must have a certain minimum size in order to be effective. According to a first rule, it should not be less than 0.1 times, expediently 0.2 times the volume of the pressure space. According to another rule, it should be at least as large, expediently twice as large as the third power of the clear pressure nozzle diameter at the height of its connecting flange.
In Fig. 1 ist dargestellt, welchen Einfluß die erfindungsgemäßen Maßnahmen auf den Schalldruck in der Umgebung einer Versuchspumpe, die aus Vakuum gegen die Atmosphäre verdichtet, ausübt. Im Maximumbereich konnte der Schalldruck um mehr als 10 dB(A) gesenkt werden.1 shows the influence of the measures according to the invention on the sound pressure in the environment Test pump, which compresses from the vacuum against the atmosphere. In the maximum range, the sound pressure could be reduced by more than 10 dB (A).
Eine besonders einfache Form der Ausführung des Pufferraums ist die Einfügung einer oder mehrerer wandbildender Teile, vorzugsweise Rippen, im Druckraum der Pumpe. Vorteilhaft ist es weiterhin, wenn diese annähernd senkrecht zur Gehäuse-Querebene, d. h. achsparallel angebracht werden. Das vereinfacht den Einbau bzw. erleichtert die Herstellung, wenn es sich bei dem Gehäuseteil um ein Gußstück handelt.A particularly simple form of the design of the buffer space is the insertion of one or more wall-forming parts, preferably ribs, in the pressure space of the pump. It is also advantageous if these are approximately perpendicular to the transverse plane of the housing, ie. H. be attached axially parallel. This simplifies installation or simplifies manufacture if the housing part is a casting.
Bei manchen Flüssigkeitsringpumpen sind zusätzlich zu dem ständig offenen Druckschlitz des Förderraums durch Ventile verschließbare Drucköffnungen vorgesehen, wobei gegebenenfalls für die Bildung oder Halterung der Ventile besondere Gehäuseteile vorgesehen werden, die einen gewissen Platz beanspruchen. Es kann auf Schwierigkeiten stoßen, zusätzlich dazu im Druckraum auch noch einen Pufferraum zu schaffen. Erfindungsgemäß läßt sich diese Schwierigkeit dadurch vermeiden oder vermindern, daß die Ventilöffnungen oder wenigstens einige von ihnen (nämlich vorzugsweise diejenigen, die in Umlaufrichtung zuerst von den Flügeln des Flügelrads erreicht werden) in den Pufferraum einbezogen werden. Lediglich das aus dem ständig offenen Teil des Druckschlitzes austretende Gasflüssigkeitsgemisch beziehungsweise gegebenenfalls das aus den nicht in den Pufferraum einbezogene Ventilöffnungen austretende Gasflüssigkeitsgemisch wird dann an dem Pufferraum vorbeigeleitet. Die Forderung der Erfindung, daß der Pufferraum außer seiner dem Strömungsweg zugewendeten Öffnung im wesentlichen geschlossen sein soll, wird gleichwohl erfüllt, weil die Ventilöffnungen (bzw. zumindest die der Umlaufrichtung entgegen vorne liegenden Ventilöffnungen) bei denjenigen Ansaugdrücken, bei denen die stärkste Geräuschentwicklung stattfindet, betriebsbedingt geschlossen sind.In some liquid ring pumps, pressure openings which can be closed by valves are provided in addition to the constantly open pressure slot in the delivery chamber, special housing parts which require a certain space being provided for the formation or mounting of the valves. It can be difficult to create a buffer space in addition to the pressure space. According to the invention, this difficulty can be avoided or reduced by including the valve openings or at least some of them (namely preferably those which are first reached in the direction of rotation by the vanes of the impeller) in the buffer space. Only the gas-liquid mixture emerging from the constantly open part of the pressure slot or, if appropriate, the gas-liquid mixture emerging from the valve openings not included in the buffer space is then directed past the buffer space. The requirement of the invention that the buffer space should be essentially closed in addition to its opening facing the flow path is nevertheless met because the valve openings (or at least the valve openings lying at the front in the direction of rotation) at those suction pressures at which the greatest noise development occurs. are closed for operational reasons.
Eine weitere besonders einfache Form der Ausführung der Erfindung ist es, wenn man vom Druckstutzen ausgehend ein doppelwandiges Rohr in den Druckraum der Pumpe hineinführt und den Zwischenraum zwischen den beiden Rohrwänden nach oben abschließt, nach unten hin aber offenläßt.Another particularly simple form of the embodiment of the invention is when a double-walled pipe is led into the pressure chamber of the pump from the pressure port and closes the space between the two pipe walls at the top, but leaves it open at the bottom.
Die Größe der Pufferraumöffnung sollte auch ein gewisses Mindestmaß im Verhältnis zur Stärke des Förderstroms haben, die näherungsweise durch den Druckstutzenquerschnitt in Höhe des Anschlußflanschs repräsentiert wird. Das Verhältnis der Größe der Pufferraumöffnung zu diesem Druckstutzenquerschnitt sollte zwischen 0,2 und 5, vorzugsweise zwischen 0,5 und 2 liegen.The size of the buffer chamber opening should also have a certain minimum dimension in relation to the strength of the delivery flow, which is approximately represented by the cross-section of the discharge nozzle at the level of the connecting flange. The ratio of the size of the buffer space opening to this pressure port cross section should be between 0.2 and 5, preferably between 0.5 and 2.
Die Erfindung wird im folgenden näher unter Bezugnahme auf die Figuren II bis VI erläutert, die vorteilhafte Ausführungsbeispiele in schematischen Querschnitten veranschaulichen.The invention is explained in more detail below with reference to FIGS. II to VI, which illustrate advantageous exemplary embodiments in schematic cross sections.
Im Beispiel gemäß Figur II befindet sich der Druckraum 3 in der linken Gehäusehälfte. Das Gasflüssigkeitsgemisch tritt durch den ständig offenen Druckschlitz 2 in den Druckraum 3 ein und verläßt ihn durch den Druckstutzen 1. Durch Wände 5 ist innerhalb des Druckraums 3 der Pufferraum 4 abgeteilt, der sich im wesentlichen vertikal erstreckt und dessen vertikale Länge etwa doppelt so groß ist wie seine größte horizontale Weite. Man muß sich vorstellen, daß seine Wände 5 sich über die gesamte axiale Abmessung des Druckraums zwischen seinen vor und hinter der Darstellungsebene befindlichen Begrenzungswänden erstrecken oder durch eine parallel zur Darstellungsebene verlaufende, zusätzliche Wand geschlossen sind. In den Pufferraum 4 münden die durch Ventile abschließbaren Drucköffnungen 6. In denjenigen Betriebsbereichen, in denen die Geräusche hauptsächlich entstehen, sind diese Öffnungen geschlossen, wobei der aus dem Druckschlitz 2 austretende Gasflüssigkeitsstrom auf seinem Weg zum Druckstutzen 1 an der unten befindlichen Öffnung des Pufferraums 4 vorbei geführt wird.In the example according to FIG. II, the
Im Ausführungsbeispiel der Figur 3 ist um den tief in den Druckraum 3 hinabragenden Druckstutzen 1 herum durch die Wand 5 und die links vom Druckstutzen befindliche Gehäusewand ein Pufferraum geschaffen, dessen Höhe mehrfach größer ist als seine in der Darstellung ersichtliche Öffnungsweite. Im übrigen sind die Erläuterungen zu Figur II auf dieses Beispiel übertragbar.In the exemplary embodiment in FIG. 3, a buffer space is created around the
Dies gilt auch für das Beispiel gemäß Figur IV, in welchem der Pufferraum als Zwischenraum zwischen zwei konzentrischen Rohren gebildet ist, von denen das Innere den Druckstutzen bildet.This also applies to the example according to FIG. IV, in which the buffer space is formed as an intermediate space between two concentric tubes, of which the interior forms the pressure connection.
Im Ausführungsbeispiel gemäß Figur V erstreckt sich der Druckraum über den gesamten Querschnitt des Gehäuses. Zwischen dem Bereich, in welchem der ständig offene Teil des Druckschlitzes 2 angeordnet ist, und dem Druckstutzen 1 ist durch Wände 5 ein Pufferraum gebildet, dessen Höhe vielfach größer ist als seine größte, in der Darstellungsebene erscheinende Weite. Dasselbe gilt für das Beispiel gemäß Figur VI, wobei zwischen der nach unten gewendeten Öffnung des Pufferraums und dem nahe dieser Öffnung gelegenen, ständig offenen Druckschlitz 2 eine von unten nach oben sich erstreckende Trennrippe angeordnet ist, die die Pufferraumöffnung von dem Druckschlitz abschirmt und dafür sorgt, daß der Förderstrom beruhigt und ohne wesentliche in den Pufferraum gerichtete Strömungskomponente daran vorbeifließt.In the exemplary embodiment according to FIG. V, the pressure space extends over the entire cross section of the housing. Between the area in which the constantly open part of the
Claims (9)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE9314146U | 1993-09-18 | ||
| DE9314146U DE9314146U1 (en) | 1993-09-18 | 1993-09-18 | Liquid ring gas pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0644332A1 true EP0644332A1 (en) | 1995-03-22 |
| EP0644332B1 EP0644332B1 (en) | 1997-01-15 |
Family
ID=6898283
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP94114730A Expired - Lifetime EP0644332B1 (en) | 1993-09-18 | 1994-09-19 | Liquid ring gas pump with noise suppression device |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0644332B1 (en) |
| AT (1) | ATE147837T1 (en) |
| DE (2) | DE9314146U1 (en) |
| DK (1) | DK0644332T3 (en) |
| ES (1) | ES2098840T3 (en) |
| GR (1) | GR3023140T3 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1083945C (en) * | 1996-07-18 | 2002-05-01 | 三洋电机株式会社 | Rotary compressor |
| EP1647713A3 (en) * | 2004-10-15 | 2012-10-24 | CNH Italia S.p.A. | Fluid pumping apparatus with Helmholtz-resonator |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2036295A1 (en) * | 1970-07-22 | 1972-01-27 | Siemen & Hinsch Gmbh | Liquid ring compressor with noise reduction |
| DE2752261A1 (en) * | 1977-11-23 | 1979-06-07 | Bosch Gmbh Robert | SILENCER FOR GAS-SHAPED OPERATING EQUIPMENT ESCAPED |
| JPS5946383A (en) * | 1982-09-10 | 1984-03-15 | Nippon Denso Co Ltd | Enclosed type compressor |
| JPS59105980A (en) * | 1982-12-10 | 1984-06-19 | Toshiba Corp | Enclosed type compressor |
| US4781545A (en) * | 1985-09-30 | 1988-11-01 | Kabushiki Kaisha Toshiba | Rotary compressor with sound suppression tubular cavity section |
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1993
- 1993-09-18 DE DE9314146U patent/DE9314146U1/en not_active Expired - Lifetime
-
1994
- 1994-09-19 AT AT94114730T patent/ATE147837T1/en not_active IP Right Cessation
- 1994-09-19 DE DE59401589T patent/DE59401589D1/en not_active Expired - Lifetime
- 1994-09-19 ES ES94114730T patent/ES2098840T3/en not_active Expired - Lifetime
- 1994-09-19 DK DK94114730.8T patent/DK0644332T3/en active
- 1994-09-19 EP EP94114730A patent/EP0644332B1/en not_active Expired - Lifetime
-
1997
- 1997-04-15 GR GR970400802T patent/GR3023140T3/en unknown
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2036295A1 (en) * | 1970-07-22 | 1972-01-27 | Siemen & Hinsch Gmbh | Liquid ring compressor with noise reduction |
| DE2752261A1 (en) * | 1977-11-23 | 1979-06-07 | Bosch Gmbh Robert | SILENCER FOR GAS-SHAPED OPERATING EQUIPMENT ESCAPED |
| JPS5946383A (en) * | 1982-09-10 | 1984-03-15 | Nippon Denso Co Ltd | Enclosed type compressor |
| JPS59105980A (en) * | 1982-12-10 | 1984-06-19 | Toshiba Corp | Enclosed type compressor |
| US4781545A (en) * | 1985-09-30 | 1988-11-01 | Kabushiki Kaisha Toshiba | Rotary compressor with sound suppression tubular cavity section |
Non-Patent Citations (2)
| Title |
|---|
| PATENT ABSTRACTS OF JAPAN vol. 8, no. 148 (M - 308) 11 July 1984 (1984-07-11) * |
| PATENT ABSTRACTS OF JAPAN vol. 8, no. 224 (M - 331) 13 October 1984 (1984-10-13) * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1083945C (en) * | 1996-07-18 | 2002-05-01 | 三洋电机株式会社 | Rotary compressor |
| EP1647713A3 (en) * | 2004-10-15 | 2012-10-24 | CNH Italia S.p.A. | Fluid pumping apparatus with Helmholtz-resonator |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0644332B1 (en) | 1997-01-15 |
| DK0644332T3 (en) | 1997-07-21 |
| GR3023140T3 (en) | 1997-07-30 |
| ATE147837T1 (en) | 1997-02-15 |
| DE59401589D1 (en) | 1997-02-27 |
| DE9314146U1 (en) | 1995-01-26 |
| ES2098840T3 (en) | 1997-05-01 |
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